Combustion chamber test piece and side wall structure thereof

Abstract

The invention discloses a combustion chamber test piece and a side wall structure thereof, and relates to the technical field of combustion chambers. The side wall structure comprises a front connecting flange and a rear connecting flange, the casing side wall is arranged between the front connecting flange and the rear connecting flange; the simulation side wall is movably arranged on the casing side wall; a first gap and a second gap are formed between the casing side wall and the simulation side wall; the first gap is a gap between the casing side wall and the simulation side wall along the axial direction of the combustion chamber test piece; and the second gap is a gap between the casing side wall and the simulation side wall along the radial direction of the combustion chamber test piece. The side wall is divided into the casing side wall and the simulation side wall, and the axial first gap and the radial second gap are arranged between the casing side wall and the simulation side wall, so that the problem of thermal stress caused by non-uniform temperature distribution of the side wall structure during the test can be solved in a targeted manner.

Description

Technical Field

[0001] This application relates to the field of combustion chamber technology, specifically to a combustion chamber test piece and its sidewall structure. Background Technology

[0002] When conducting single-head tests on annular combustion chambers (e.g., gas turbine combustion chambers or aero-engine combustion chambers), sidewall structures are typically installed on both sides of the single-head combustion chamber to more realistically simulate the high-temperature gas flow within the combustion chamber, forming a combustion chamber test specimen (e.g., Figure 17 (As shown). During simulation testing, since combustion only occurs inside the flame tube, the temperature distribution inside the combustion chamber test piece becomes uneven (for example, the sidewall structure closer to the flame tube experiences a higher heat load and correspondingly higher thermal stress; while the sidewall structure farther from the flame tube, closer to the connecting flanges (such as the front and rear connecting flanges mentioned below), experiences a lower heat load and correspondingly lower thermal stress). This uneven distribution of thermal stress can lead to plastic deformation and even cracking of the sidewall structure, seriously affecting the reliability and service life of the combustion chamber test piece. Currently, a common solution to this problem is to use thermal barrier coatings to mitigate the high-temperature ablation of the sidewall structure. However, this method only supports short-term tests; in long-term tests, the sidewall structure will still exhibit significant plastic deformation and cracking damage. Summary of the Invention

[0003] The purpose of this application is to provide a combustion chamber test specimen and its sidewall structure to solve the technical problem that the sidewall structure of existing combustion chamber test specimens is prone to plastic deformation or cracking and other damage.

[0004] To achieve the above objectives, this application provides the following technical solution:

[0005] Firstly, this application proposes a technical solution for a sidewall structure of a combustion chamber test piece, the sidewall structure comprising:

[0006] Front connecting flange and rear connecting flange;

[0007] The casing sidewall is located between the front connecting flange and the rear connecting flange;

[0008] A simulated sidewall is movably disposed on the casing sidewall; and a first gap and a second gap are formed between the casing sidewall and the simulated sidewall; the first gap is the gap between the casing sidewall and the simulated sidewall along the axial direction of the combustion chamber test piece; the second gap is the gap between the casing sidewall and the simulated sidewall along the radial direction of the combustion chamber test piece.

[0009] As a specific embodiment of the technical solution in this application, the front end of the casing sidewall is movably inserted into the front connecting flange, and a third gap is formed between the casing sidewall and the front connecting flange, the third gap being the gap between the casing sidewall and the front connecting flange along the axial direction of the combustion chamber test piece; the rear end of the casing sidewall is fixedly connected to the rear connecting flange; and / or, the rear end of the casing sidewall is movably inserted into the rear connecting flange, and a fourth gap is formed between the casing sidewall and the rear connecting flange, the fourth gap being the gap between the casing sidewall and the rear connecting flange along the axial direction of the combustion chamber test piece; the rear end of the casing sidewall is fixedly connected to the front connecting flange.

[0010] As a specific solution in this application, the connecting edges of the casing sidewall and the simulated sidewall are both stepped, so that the casing sidewall and the simulated sidewall can be movably overlapped.

[0011] As a specific embodiment of the technical solution in this application, the stepped edge opening of the casing sidewall faces the outside of the combustion chamber test piece; the stepped edge opening of the simulated sidewall faces the inside of the combustion chamber test piece; the sidewall structure also includes a plurality of elastic members, each elastic member being distributed circumferentially around the simulated sidewall, and one end of each elastic member being connected to the outer wall surface of the casing sidewall, and the other end of each elastic member abutting against the outer wall surface of the simulated sidewall.

[0012] As a specific solution in this application, the elastic element includes a straight section and a bending elastic section connected in sequence.

[0013] As a specific embodiment of the technical solution in this application, the first gap is larger than the second gap; the ratio of the first gap to the second gap is equal to the ratio of the length to the width of the simulated sidewall.

[0014] As a specific solution in this application, the sidewall structure further includes:

[0015] A cooling sidewall is disposed on the outer wall surface of the simulated sidewall; a cooling cavity is formed between the cooling sidewall and the simulated sidewall; the cooling cavity covers the high-temperature area of ​​the simulated sidewall during the test;

[0016] Both the air inlet pipe and the air outlet pipe are located on the cooling sidewall, and both the air inlet pipe and the air outlet pipe are connected to the cooling chamber.

[0017] As a specific solution in this application, the cooling cavity is further provided with a plurality of cooling ribs; each cooling rib is provided on the outer wall surface of the simulated sidewall, and each cooling rib is distributed sequentially along a first direction; the first direction is parallel to the flow direction of the airflow in the cooling cavity.

[0018] As a specific solution in this application, the extension direction of each cooling rib is perpendicular to the first direction, and the cross-section of each cooling rib is hexagonal.

[0019] As a specific embodiment of the technical solution in this application, each cooling rib is provided with multiple cooling holes; the angle between the axis of each cooling hole and the outer wall surface of the simulated sidewall is greater than or equal to 25° and less than or equal to 45°; the distance between the front end of each cooling hole and the outer wall surface of the simulated sidewall is greater than the distance between the rear end of the cooling hole and the outer wall surface of the simulated sidewall.

[0020] As a specific embodiment of the technical solution in this application, an intake pressure regulator is further provided between the intake pipe and the cooling sidewall; the intake pressure regulator has an intake pressure regulating cavity inside; the intake pipe is connected to the cooling cavity through the intake pressure regulating cavity; the intake pressure regulating cavity is at least used to reduce the eddies formed when fluid located outside the cooling cavity enters the interior of the cooling cavity.

[0021] As a specific embodiment of the technical solution in this application, the front end of the intake regulator is in the shape of a round tube, and the rear end is in the shape of a flat tube.

[0022] As a specific embodiment of the technical solution in this application, the width of the connection between the intake pressure regulating chamber and the cooling chamber is equal to the height of the cooling chamber.

[0023] As a specific embodiment of the technical solution in this application, an exhaust pressure regulator is further provided between the exhaust pipe and the cooling sidewall; the exhaust pressure regulator has an exhaust pressure stabilizing cavity inside; the exhaust pipe is connected to the cooling cavity through the exhaust pressure stabilizing cavity; the exhaust pressure stabilizing cavity is at least used to reduce the eddies formed when the fluid inside the cooling cavity flows out of the cooling cavity.

[0024] Secondly, this application proposes a technical solution for a combustion chamber test piece, which includes a sidewall structure as described in any one of the first aspects.

[0025] Compared with the prior art, the beneficial effects of this application are:

[0026] This application addresses the thermal stress problem caused by uneven temperature distribution in the sidewall structure during testing by dividing the sidewall into a casing sidewall and a simulated sidewall, and by setting an axial first gap and a radial second gap between the casing sidewall and the simulated sidewall. During testing, the simulated sidewall directly contacts the high-temperature combustion gas, resulting in a large thermal expansion amplitude. Conversely, the casing sidewall does not directly contact the high-temperature combustion gas, resulting in a smaller thermal expansion amplitude. The first and second gaps provide buffer space for the differential expansion of the casing sidewall and the simulated sidewall, preventing stress accumulation due to mutual compression, effectively preventing plastic deformation or cracking of the sidewall structure, ensuring the structural reliability of the combustion chamber test piece, and extending its service life. Attached Figure Description

[0027] Figure 1 This is a plan view of a combustion chamber test specimen proposed in an embodiment of this application;

[0028] Figure 2 for Figure 1 A cross-sectional view of the combustion chamber test specimen along the CC line;

[0029] Figure 3 for Figure 1 Another cross-sectional view of the combustion chamber test piece along the CC line;

[0030] Figure 4 for Figure 1 Another cross-sectional view of the combustion chamber test piece along the CC line;

[0031] Figure 5 for Figure 1 Enlarged view of section B;

[0032] Figure 6 for Figure 1 A schematic cross-sectional view of the combustion chamber test specimen along line AA;

[0033] Figure 7 for Figure 6 Enlarged view of section D;

[0034] Figure 8 This is a three-dimensional schematic diagram of a simulated sidewall proposed in an embodiment of this application;

[0035] Figure 9 This is a cross-sectional schematic diagram of a simulated sidewall proposed in an embodiment of this application;

[0036] Figure 10 for Figure 9 A schematic diagram of the flow path of the cooling gas in the embodiment;

[0037] Figure 11 for Figure 9The simulated sidewall is shown in the cross-sectional view along the FF line.

[0038] Figure 12 for Figure 11 A magnified view of section K in the middle;

[0039] Figure 13 for Figure 12 A cross-sectional view of the intermediate cooling ribs along the MM line;

[0040] Figure 14 for Figure 9 A schematic cross-sectional view of the simulated sidewall along the GG line;

[0041] Figure 15 This is a contour plot of the convective heat transfer coefficient of a sidewall proposed in an embodiment of this application;

[0042] Figure 16 This is another simulation of the convective heat transfer coefficient contour plot of the sidewall proposed in the embodiments of this application;

[0043] Figure 17 A cross-sectional schematic diagram of a combustion chamber test specimen in the prior art.

[0044] In the diagram: 1. Front connecting flange; 2. Rear connecting flange; 3. Casing side wall; 4. Simulated side wall; 5. Elastic element; 41. Cooling rib; 42. Cooling hole; 51. Straight section; 52. Bending elastic section; 61. Inlet pipe; 62. Outlet pipe; 7. Cooling side wall; 71. Cooling chamber; 8. Inlet pressure regulator; 81. Inlet pressure regulator chamber; 9. Outlet pressure regulator; 91. Outlet pressure regulator chamber; 10. Casing; 11. Flame tube. Detailed Implementation

[0045] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0046] It should be noted that in the description of this application, the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application 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. Therefore, they should not be construed as limitations on this application.

[0047] Furthermore, it should be understood that, for ease of description, the dimensions of the various components shown in the accompanying drawings are not drawn to actual scale; for example, the thickness or width of some layers may be exaggerated relative to other layers.

[0048] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined or described in one figure, it will not need to be discussed or described in detail in the description of the subsequent figures.

[0049] It is important to understand that an annular combustor is formed by multiple single-head combustors arranged in a ring. Each single-head combustor is an independent functional unit constituting the annular combustor. That is, each single-head combustor includes key combustion components such as a nozzle, a combustion head, and a flame tube, and can independently complete basic tasks such as fuel injection, mixing, and combustion. Since the single-head combustor is the basic functional module of the annular combustor, it can be used as a standalone test object. By configuring sidewall structures on both sides of it to form a complete combustor test specimen, the key operating conditions such as high-temperature gas flow and combustion efficiency of a single combustion unit (i.e., a single-head combustor) in the annular combustor during actual operation can be accurately simulated. This provides data support for the overall design optimization and performance verification of the annular combustor.

[0050] It should be noted that in this application, the components or structures (e.g., intake regulator 8 and cooling holes 42) used to guide fluid (e.g., high-temperature combustion gas or cooling gas) in the combustion chamber test piece are defined as having a front end and a rear end. The front end refers to the end where the fluid flows into the component or structure, while the rear end refers to the end where the fluid flows out of the component or structure. In other words, in the combustion chamber test piece proposed in the embodiments of this application, the flow direction of the fluid during use is always from the front end to the rear end of a certain component or structure.

[0051] It should be noted that the core improvement direction of this application focuses on the sidewall structure of the combustion chamber test specimen, specifically on the structural design and optimization of related components such as the casing sidewall and the simulated sidewall. The aim is to solve the technical problem in the prior art where uneven temperature distribution in the sidewall structure of the combustion chamber test specimen causes thermal stress, leading to plastic deformation or cracking, affecting test reliability and service life. Therefore, the embodiments only emphasize the components and connections directly related to the sidewall structure improvement, and do not present in detail conventional components such as the nozzle and combustion head of a single-head combustion chamber. The specific structure, assembly method, and basic working principle of such conventional components are mature technologies in the field of combustion chamber technology and can be directly referred to in existing technical solutions; therefore, they will not be elaborated upon in this application.

[0052] To address the technical problem mentioned in the background art that the sidewall structure of existing combustion chamber test specimens is prone to plastic deformation or cracking, this application proposes an embodiment of a sidewall structure for a combustion chamber test specimen. Specifically, the sidewall structure includes a front connecting flange 1, a rear connecting flange 2, a casing sidewall 3, and a simulated sidewall 4. Wherein, as... Figures 1 to 4 As shown, the casing sidewall 3 is disposed between the front connecting flange 1 and the rear connecting flange 2. The simulated sidewall 4 is movably disposed on the casing sidewall 3, and a first gap is formed between the casing sidewall 3 and the simulated sidewall 4 (i.e., as shown in the figure). Figure 5 The gap S1 shown) and the second gap (i.e., as shown) Figure 5 The gap H1 shown is defined as follows: the first gap is the gap between the casing sidewall 3 and the simulated sidewall 4 along the axial direction of the combustion chamber test piece; the second gap is the gap between the casing sidewall 3 and the simulated sidewall 4 along the radial direction of the combustion chamber test piece.

[0053] In this embodiment, as Figure 6 As shown, the purpose of setting the casing sidewall 3 is to establish a fan-shaped space corresponding to the combustion chamber test piece using the casing sidewall 3, so as to ensure that the air flow field during the single-head combustion chamber test is similar to the air flow field in the annular combustion chamber.

[0054] In this embodiment, as Figure 6 As shown, the purpose of setting up the simulated sidewall 4 is to establish the combustion environment of the flame tube in the single-head combustion chamber, so that the internal flow field and combustion organization of the flame tube in the single-head combustion chamber are similar to those in the annular combustion chamber during the test.

[0055] When conducting a single-head test, if the combustion chamber test piece is constructed using the sidewall structure proposed in this application embodiment, then during combustion in the flame tube, because the simulated sidewall 4 is in direct contact with the high-temperature gas in the flame tube, the temperature rise of the simulated sidewall 4 is relatively large, resulting in a significant expansion; because the casing sidewall 3 is not in direct contact with the high-temperature gas in the flame tube, the temperature rise of the casing sidewall 3 is relatively small, resulting in a smaller expansion. In this embodiment, because a first gap is formed between the casing sidewall 3 and the simulated sidewall 4 (i.e., as... Figure 5 The gap S1 shown) and the second gap (i.e., as shown) Figure 5 As shown in the gap H1, the first and second gaps provide buffer space for the differential expansion of the casing sidewall 3 and the simulated sidewall 4, preventing them from squeezing each other due to the differential expansion. This ensures that the simulated sidewall 4 expands without constraint, preventing thermal stress from accumulating between the casing sidewall 3 and the simulated sidewall 4, thereby solving the problem of plastic deformation or cracking of the sidewall structure due to excessive thermal stress.

[0056] Based on the heat load generated during the combustion chamber test, this embodiment designs the sidewall structure into two parts: a casing sidewall and a simulated sidewall. A first gap and a second gap are formed between the casing sidewall and the simulated sidewall to eliminate differential expansion between the casing sidewall and the simulated sidewall. This avoids the accumulation of thermal stress at the connection between the casing sidewall and the simulated sidewall, effectively reducing the risk of plastic deformation or cracking of the sidewall structure and extending the service life of the combustion chamber test piece.

[0057] In this embodiment, as Figure 1 and Figure 5 As shown, the purpose of setting the first gap is to eliminate the differential expansion along the axial direction of the single-head combustion chamber (i.e., the axial direction of the combustion chamber test piece) generated by the casing sidewall 3 and the simulated sidewall 4 during the test; the purpose of setting the second gap is to eliminate the differential expansion along the radial direction of the single-head combustion chamber (i.e., the radial direction of the combustion chamber test piece) generated by the casing sidewall 3 and the simulated sidewall 4 during the test.

[0058] It is important to note that during the operation of the combustion chamber test specimen, the thermal expansion of the simulated sidewall 4 differs significantly between the axial and radial directions. Compared to the width of the simulated sidewall 4 along the radial direction (hereinafter referred to as the first radial direction), the length of the simulated sidewall 4 along the axial direction (hereinafter referred to as the first axial direction) is much longer. Therefore, after heating, the expansion of the simulated sidewall 4 along the first axial direction is significantly greater than the expansion along the first radial direction. If the size relationship between the first gap and the second gap is not specifically designed, two problems may arise: one is that the first gap is insufficient, unable to fully accommodate the expansion of the simulated sidewall 4 along the first axial direction, leading to thermal stress caused by mutual compression between the simulated sidewall 4 and the casing sidewall 3; the other is that the second gap is too large, compressing the internal flow field sealing of the combustion chamber test specimen, causing high-temperature gas leakage, and affecting the accuracy of the test data. To ensure that the first gap and the second gap can match the differentiated expansion requirements of the simulated sidewall 4, avoiding compression damage along the first axial direction while maintaining the internal flow field sealing of the combustion chamber test specimen, in one embodiment of this application, the first gap can be larger than the second gap.

[0059] As mentioned above, if the first gap is insufficient, it cannot fully accommodate the expansion of the simulated sidewall 4 along the first axial direction; if the second gap is too large, it will compromise the sealing of the internal flow field of the combustion chamber test piece. To ensure that the first and second gaps precisely match the differentiated expansion requirements of the simulated sidewall 4, in one embodiment of this application, the ratio of the first gap to the second gap can be equal to the ratio of the length to the width of the simulated sidewall 4. In this embodiment, the length direction of the simulated sidewall 4 is parallel to the first axial direction, and the width direction of the simulated sidewall 4 is parallel to the first radial direction.

[0060] In the embodiments of this application, the connection relationship between the casing sidewall 3 and the simulated sidewall 4 is not limited, as long as a first gap and a second gap can be formed between the casing sidewall 3 and the simulated sidewall 4. For example, the casing sidewall 3 and the simulated sidewall 4 can be as follows: Figure 2 As shown, the connecting edges of the casing sidewall 3 and the simulated sidewall 4 are both planar; or, they can be as follows: Figure 3 As shown, the connecting edge of the simulated sidewall 4 is provided with a groove, and the connecting edge of the casing sidewall 3 and the groove of the connecting edge of the simulated sidewall 4 form a snap-fit ​​(in other embodiments, the groove can also be provided on the connecting edge of the casing sidewall 3, which will not be elaborated here); or, it can be as follows Figure 4 As shown, the connecting edges of the casing sidewall 3 and the simulated sidewall 4 are both stepped, so that the casing sidewall 3 and the simulated sidewall 4 can form a movable overlap.

[0061] It should be clear that the connecting edges of the casing sidewall 3 and the simulated sidewall 4 are both planar (i.e., as shown in the image). Figure 2 In the embodiment shown, the stepped edges of the casing sidewall 3 and the simulated sidewall 4 can contact each other through the stepped plane, significantly reducing gas outflow from the combustion chamber test piece during testing, ensuring the stability and sealing of the internal flow field of the combustion chamber test piece, and thus improving the accuracy of the test data. Simultaneously, the stepped overlapping structure provides more precise guidance for the relative displacement caused by the thermal expansion of the casing sidewall 3 and the simulated sidewall 4, preventing misalignment of the connecting edges of the casing sidewall 3 and the simulated sidewall 4. A groove is provided relative to the connecting edge of the simulated sidewall 4, and the connecting edge of the casing sidewall 3 and the groove of the connecting edge of the simulated sidewall 4 form a snap-fit ​​(i.e., as shown). Figure 3 The embodiment shown has stepped edges connecting the casing sidewall 3 and the simulated sidewall 4 (i.e., as shown in the example). Figure 4 The embodiment shown can be used in conjunction with the elastic element 5 described below to reduce the thermal stress generated in the single-head combustion chamber along the circumference of the single-head combustion chamber during the test.

[0062] It should be noted that the single-head combustion chamber in the combustion chamber test piece is obtained by cutting a single independent combustion unit from a complete annular combustion chamber. Therefore, the circumferential integrity of the single-head combustion chamber is disrupted. During thermal expansion, the two sides of the single-head combustion chamber are no longer subject to uniform mutual restraint as in the annular combustion chamber, but instead expand freely outwards circumferentially from both sides. During the single-head test, the combustion temperature inside the flame tube can reach over 1800°C. If the casing sidewall 3 and the simulated sidewall 4 are rigidly fixed along the circumference of the combustion chamber test piece (i.e., the circumference of the single-head combustion chamber), the simulated sidewall 4 cannot expand to both sides along the circumference of the combustion chamber test piece (hereinafter referred to as the first circumferential direction), which may still cause stress concentration in the casing sidewall 3 and the simulated sidewall 4 along the first circumferential direction. Based on this, in one embodiment of this application, such as... Figure 2As shown, the stepped edge opening of the casing sidewall 3 faces the outside of the combustion chamber test piece (e.g., Figure 4 As shown, direction Q is the direction towards the outside of the combustion chamber test piece; the stepped edge opening of the simulated sidewall 4 faces the inside of the combustion chamber test piece (e.g., Figure 4 As shown, direction P is the direction towards the inside of the combustion chamber test piece. Figure 1 , Figure 6 and Figure 7 As shown, the sidewall structure also includes multiple elastic elements 5, each elastic element 5 being distributed circumferentially around the simulated sidewall 4, with one end of each elastic element 5 connected to the outer wall surface of the casing sidewall 3, and the other end of each elastic element 5 abutting against the outer wall surface of the simulated sidewall 4. Of course, in other embodiments of this application, one end of each elastic element 5 may be connected to the inner wall surface of the simulated sidewall 4, and the other end of each elastic element 5 may abut against the inner wall surface of the casing sidewall 3.

[0063] In use, if the single-head combustion chamber expands to both sides along the first circumference when heated, that is, the simulated sidewall 4 will move outward synchronously with the expansion trend of the single-head combustion chamber (i.e., as...). Figure 4 As shown, the simulated sidewall 4 moves along direction Q. The stepped overlapping edge of the casing sidewall 3 and the simulated sidewall 4 provides smooth guidance for the circumferential displacement of the simulated sidewall 4, preventing mechanical jamming between the casing sidewall 3 and the simulated sidewall 4. Simultaneously, the elastic element 5 undergoes elastic deformation under the compression of the simulated sidewall 4. Unlike rigid fixation, it does not hinder the expansion of the simulated sidewall 4 along the first circumferential direction, and it can also provide flexible restraint for the simulated sidewall 4 through elastic restoring force, preventing excessive displacement that could lead to sealing failure of the internal flow field of the combustion chamber. This combination of movable overlap and elastic buffer design effectively releases the thermal expansion stress along the first circumferential direction of the single-head combustion chamber during the test, avoids stress concentration problems caused by rigid constraints, reduces the risk of deformation and cracking of the casing sidewall 3 and the simulated sidewall 4, and ensures the structural stability and test safety of the combustion chamber test piece.

[0064] Of course, in other embodiments of this application, it is not only the stepped edges of the casing sidewall 3 and the simulated sidewall 4 that allow the elastic member 5 to form a flexible connection between the casing sidewall 3 and the simulated sidewall 4 along the first circumference upward. For example, as... Figure 2 and Figure 7 As shown, when the connecting edges of the casing sidewall 3 and the simulated sidewall 4 are both planar, the elastic element 5 can also be used to make the casing sidewall 3 and the simulated sidewall 4 form a flexible connection along the first circumference.

[0065] In the embodiments of this application, the shape and structure of the elastic element 5 are not limited, as long as the elastic element 5 can enable the casing sidewall 3 and the simulated sidewall 4 to form a flexible connection along the first circumferential direction. For example, the elastic element 5 can be as follows: Figure 2and Figure 4 The ones shown are in the form of straight sheets; or, they can also be as shown in the image. Figure 7 As shown, the elastic element 5 includes a straight section 51 and a curved elastic section 52 connected in sequence.

[0066] In one embodiment of this application, the straight section 51 may be connected to the casing sidewall 3, and the flexible section 52 may abut against the simulated sidewall 4. In another embodiment of this application, the straight section 51 may be connected to the simulated sidewall 4, and the flexible section 52 may abut against the casing sidewall 3.

[0067] In the embodiments of this application, there is no limitation on the number of elastic elements 5 used. For example, the number of elastic elements 5 can be 4, 5, 6, 7, 8, 9, or 10, etc. In the embodiments of this application, there is also no limitation on the thickness of the elastic elements 5. For example, the thickness of the elastic elements 5 can be 1mm, 2mm, or 3mm, etc.

[0068] It should be noted that during the single-head test, although the temperature rise of the casing sidewall 3 is smaller compared to the simulated sidewall 4, the thermal expansion of the casing sidewall 3 along the first axial direction is still significant due to its longer length. Since the front connecting flange 1 and the rear connecting flange 2 serve as the fixed reference components of the test piece, they need to maintain stable positions for a long time to ensure the accuracy of the test installation. If both ends of the casing sidewall 3 are rigidly connected to the front connecting flange 1 and the rear connecting flange 2, the thermal expansion of the casing sidewall 3 along the first axial direction will be constrained, resulting in concentrated thermal stress at the connection between the casing sidewall 3 and the front connecting flange 1 and / or the rear connecting flange 2. To release the concentrated thermal stress at the connection between the casing sidewall 3 and the front connecting flange 1 and / or the rear connecting flange 2 during the test, in one embodiment of this application, such as... Figure 4 As shown, the front end of the casing side wall 3 is movably inserted into the front connecting flange 1, and a third gap is formed between the casing side wall 3 and the front connecting flange 1 (i.e., as shown in the figure). Figure 4 The third gap (S3) is the gap between the casing sidewall 3 and the front connecting flange 1 along the axial direction (i.e., the first axial direction) of the combustion chamber test piece. The rear end of the casing sidewall 3 is fixedly connected to the rear connecting flange 2.

[0069] In use, if the casing sidewall 3 undergoes thermal expansion along the first axis, the front end of the casing sidewall 3 can freely expand and contract along the plug-in structure formed with the front connecting flange 1. The third gap will provide buffer space for the expansion of the casing sidewall 3 along the first axis, which can avoid the extrusion stress between the casing sidewall 3 and the front connecting flange 1, and also avoid the extrusion stress between the casing sidewall 3 and the rear connecting flange 2.

[0070] Of course, in other embodiments of this application, the rear end of the casing sidewall 3 can also be movably connected to the rear connecting flange 2, and a fourth gap is formed between the casing sidewall 3 and the rear connecting flange 2. The fourth gap is the gap between the casing sidewall 3 and the rear connecting flange 2 along the axial direction of the combustion chamber test piece. The rear end of the casing sidewall 3 is fixedly connected to the front connecting flange 1. The fourth gap can also provide a buffer space for the thermal expansion of the casing sidewall 3 along the first axial direction, and the principle is the same as that of the third gap, which will not be elaborated here.

[0071] It should be noted that during single-head testing, the internal combustion temperature of the flame tube can reach over 1800℃. The simulated sidewall 4 is in direct contact with the high-temperature combustion gas and is subjected to extremely high heat loads for extended periods. While the gap design mentioned earlier (i.e., the first to fourth gaps) can release the thermal expansion stress generated by the simulated sidewall 4, it cannot prevent the material performance degradation or localized ablation of the simulated sidewall 4 caused by high temperatures. For example, if the simulated sidewall 4 is continuously exposed to a high-temperature environment, its surface will not only age faster due to thermal oxidation but also exhibit localized melting and deformation, thereby affecting the long-term stability of the combustion chamber test piece and the consistency of test data. To further enhance the high-temperature protection capability of the simulated sidewall 4, reduce the impact of heat load on its structural integrity, extend the service life of the combustion chamber test piece, and ensure test reliability, in one embodiment of this application, the sidewall structure may further include a cooling sidewall 7, an inlet pipe 61, and an outlet pipe 62. Figure 8 and Figure 9 As shown, a cooling sidewall 7 is disposed on the outer wall surface of the simulated sidewall 4, and a cooling cavity 71 is formed between the cooling sidewall 7 and the simulated sidewall 4. The cooling cavity 71 covers the high-temperature area of ​​the simulated sidewall 4 during the test. Both the air inlet pipe 61 and the air outlet pipe 62 are disposed on the cooling sidewall 7, and both the air inlet pipe 61 and the air outlet pipe 62 are connected to the cooling cavity 71.

[0072] In this application, the inner wall surface of the simulated sidewall 4 refers to the wall surface that is in direct contact with the high-temperature gas inside the flame tube during the test; the outer wall surface of the simulated sidewall 4 refers to the wall surface that is parallel to the inner wall surface of the simulated sidewall 4, and the outer wall surface of the simulated sidewall 4 is not in direct contact with the high-temperature gas inside the flame tube during the test.

[0073] During testing, cooling gas (e.g., air or nitrogen) can be introduced into the cooling chamber 71 through the inlet pipe 61. This cooling gas in the cooling chamber 71 cools the high-temperature areas of the simulated sidewall 4, quickly removing heat from its surface to lower its overall temperature. This prevents the simulated sidewall 4 from experiencing performance degradation, thermal oxidation aging, or localized melting and deformation due to prolonged exposure to high temperatures. Furthermore, after absorbing a significant amount of heat, the cooling gas in the cooling chamber 71 is discharged through the outlet pipe 62. The inlet pipe 61, cooling chamber 71, and outlet pipe 62 form a cooling flow channel, ensuring the temperature stability of the simulated sidewall 4 during long-term testing.

[0074] In this embodiment, the high-temperature region of the simulated sidewall 4 refers to the region where the temperature of the simulated sidewall 4 is higher than a preset temperature value during the test. The preset temperature value can be set according to requirements. For example, the preset temperature value can be a fixed temperature value such as 800℃ or 1000℃; or, the preset temperature value can be a dynamically changing temperature value such as 0.5 times or 0.6 times the highest temperature (e.g., 1800℃ mentioned above) during the test of the single-head combustion chamber.

[0075] It should be noted that if the intake pipe 61 is directly connected to the cooling chamber 71, the connection point between the intake pipe 61 and the cooling chamber 71 forms a right angle. When the cooling gas enters the cooling chamber 71 through the intake pipe 61, a vortex (i.e., a backflow zone) will be formed at the right-angle connection due to the abrupt change in the flow channel cross-section and the sudden change in airflow direction. The vortex not only leads to uneven distribution of cooling gas, affecting the cooling effect of the high-temperature area of ​​the simulated sidewall 4, but also hinders the flow of cooling gas, causing insufficient local cooling or heat accumulation, which cannot meet the temperature stability requirements of the simulated sidewall 4 under long-term high-temperature conditions. In order to eliminate the above-mentioned vortex and ensure that the cooling gas can enter the cooling chamber 71 smoothly and evenly, thereby improving cooling efficiency and heat dissipation uniformity, in one embodiment of this application, an intake pressure regulator 8 is also provided between the intake pipe 61 and the cooling sidewall 7. The intake pressure regulator 8 has an intake pressure regulating chamber 81 inside, and the intake pipe 61 is connected to the cooling chamber 71 through the intake pressure regulating chamber 81. The intake pressure regulating chamber 81 is at least used to reduce the eddies formed when fluid located outside the cooling chamber 71 enters the cooling chamber 71.

[0076] In this embodiment, the shape and structure of the intake pressure regulating cavity 81 are not limited, as long as the intake pressure regulating cavity 81 can reduce the eddies formed when fluid located outside the cooling cavity 71 enters the cooling cavity 71. For example, after extensive experimental verification by the inventors, it was found that the cross-section of the intake pressure regulating cavity 81 can be crescent-shaped, elliptical, or similar. Figure 14 The example shown is a triangle with rounded apex.

[0077] In this embodiment, the flow direction of the fluid at the outlet of the intake pipe 61 can be changed by the intake pressure regulating chamber 81 (for example, changing the flow direction of the fluid at the outlet of the intake pipe 61 from parallel to the axial direction of the intake pipe 61 to intersecting the axial direction of the intake pipe 61), thereby reducing the vortex formed at the right-angle connection. Furthermore, the cross-section is crescent-shaped, elliptical, or similar. Figure 14 The triangular intake pressure regulating chamber 81 with rounded apex shown can gently change the flow direction of the fluid at the outlet of the intake pipe 61, which is not conducive to the formation of vortices.

[0078] In this embodiment, the intake regulator 8 needs to connect the intake pipe 61 and the cooling chamber 71. That is, the intake regulator 8 needs to match both the tubular airflow channel of the intake pipe 61 and the flat cavity structure of the cooling chamber 71 to ensure that the airflow remains uniform and stable when transitioning from the tubular channel to the flat cavity, avoiding uneven airflow distribution in the cooling chamber 71 due to abrupt changes in the flow channel morphology. If the airflow distribution in the cooling chamber 71 is uneven, it will lead to differences in the cooling effect of the high-temperature areas of the simulated sidewall 4. Some areas will remain at a high temperature due to insufficient cooling gas flow, leading to problems such as localized thermal stress concentration and accelerated degradation of localized material properties. In severe cases, localized melting deformation or ablation may occur, damaging the structural sealing of the combustion chamber test piece, causing high-temperature gas leakage, which not only affects the accuracy of the test data but also shortens the service life of the combustion chamber test piece and may even cause safety hazards. Therefore, in one embodiment of this application, the front end of the intake regulator 8 can be a circular tube, and the rear end of the intake regulator 8 can be a flat tube.

[0079] In this embodiment, if the front end of the intake pressure regulator 8 is in the shape of a round tube and the rear end of the intake pressure regulator 8 is in the shape of a flat tube, then the round tube-shaped front end of the intake pressure regulator 8 can be precisely matched with the intake pipe 61, reducing the resistance and impact when the airflow is introduced; the flat tube-shaped rear end of the intake pressure regulator 8 can be perfectly fitted with the inlet of the cooling chamber 71, so that the airflow is evenly diffused along the width direction of the cooling chamber 71, ensuring the consistency of the cooling effect.

[0080] It is important to note that after the cooling gas is buffered and rectified by the inlet pressure regulating chamber 81, it needs to enter the cooling chamber 71 smoothly to achieve uniform heat dissipation. The width of the connection between the inlet pressure regulating chamber 81 and the cooling chamber 71 (i.e., the width of the connection between the inlet pressure regulating chamber 81 and the cooling chamber 71) is crucial. Figure 9 The width S2 shown (hereinafter referred to as the air inlet width) and the height of the cooling cavity 71 (i.e., as shown) Figure 9The inconsistency in the height H2 (i.e., the distance between the casing sidewall 3 and the cooling sidewall 7) will lead to significant defects in the flow of cooling gas. For example, when the width of the air inlet is less than the height of the cooling cavity 71, the cooling gas will experience uneven diffusion after entering the cooling cavity 71 due to the sudden widening of the flow channel. This results in dense airflow in some areas and airflow gaps in others, failing to fully cover the high-temperature area of ​​the simulated sidewall 4. When the width of the air inlet is greater than the height of the cooling cavity 71, the cooling gas will experience compression after entering the cooling cavity 71 due to the contraction of the flow channel, leading to excessively high local flow velocity and pressure imbalance, similarly disrupting the uniformity of the airflow. Both of these situations will cause uneven heating of the simulated sidewall 4, with some areas remaining at high temperatures due to insufficient cooling, leading to problems such as thermal stress concentration and material performance degradation. Therefore, in one embodiment of this application, the width of the connection between the air inlet pressure regulating cavity 81 and the cooling cavity 71 is equal to the height of the cooling cavity 71.

[0081] During use, the cooling gas is buffered and rectified by the inlet pressure stabilizing chamber 81 and then enters the cooling chamber 71 through the flat tubular inlet. If the width of the connection between the inlet pressure stabilizing chamber 81 and the cooling chamber 71 (i.e. the width of the inlet) is consistent with the height of the cooling chamber 71, the cooling gas can flow evenly and stably in the cooling chamber 71, forming a uniform scouring effect on the entire simulated sidewall 4.

[0082] To ensure that the gas, having absorbed all its heat, can flow out of the cooling chamber 71 stably without disturbing the airflow within it, in one embodiment of this application, an outlet pressure regulator 9 is provided between the outlet pipe 62 and the cooling sidewall 7. The outlet pressure regulator 9 has an outlet pressure regulating cavity 91 inside, and the outlet pipe 62 is connected to the cooling chamber 71 through the outlet pressure regulating cavity 91. The outlet pressure regulating cavity 91 is at least used to reduce the eddies formed when the fluid inside the cooling chamber 71 flows out of the cooling chamber 71.

[0083] In this embodiment, the structure of the outlet pressure regulator 9 can be similar to that of the inlet pressure regulator 8; the structure of the outlet pressure regulator 91 can be similar to that of the inlet pressure regulator 81, which will not be described in detail here.

[0084] In this embodiment, the flow path of the cooling gas is as follows: Figure 10 The path J in the diagram is shown (to facilitate observation of the cooling gas flow path by those skilled in the art, in...). Figure 10 The attached drawings do not include the labeling for the relevant components. Figure 10 The reference numerals for the relevant components can be found in the attached diagrams. Figure 9First, cooling gas is injected into the intake pipe 61 through a cooling gas injection device (e.g., a gas compressor or a compression tank containing compressed gas); further, the cooling gas in the intake pipe 61 is buffered and rectified by the intake pressure regulator 8 before entering the cooling chamber 71; further, after absorbing heat in the cooling chamber 71, the cooling gas is buffered and rectified by the outlet pressure regulator 9 before entering the outlet pipe 62; finally, the cooled gas with increased temperature is discharged from the outlet pipe 62.

[0085] To further enhance the cooling effect of the cooling gas on the simulated sidewall 4, in one embodiment of this application, a plurality of cooling ribs 41 are also provided in the cooling cavity 71. For example... Figure 9 and Figure 11 As shown, each cooling rib 41 is disposed on the outer wall surface of the simulated sidewall 4, and the cooling ribs 41 are distributed sequentially along a first direction. The first direction is parallel to the flow direction of the airflow in the cooling cavity 71 (i.e., Figure 9 , Figure 11 and Figure 13 (direction E in the middle).

[0086] In this embodiment, the arrangement of multiple cooling ribs 41 increases the contact area between the simulated sidewall 4 and the cooling gas, extending the residence time of the cooling gas within the cooling chamber 71 and allowing for more thorough heat exchange. Furthermore, the cooling ribs 41, distributed along the airflow direction (i.e., the first direction), guide and organize the cooling airflow (i.e., the airflow diffuses evenly along the extension direction of the cooling ribs 41 after encountering them), preventing turbulent airflow that could lead to uneven cooling. In other words, the design of the cooling ribs 41 improves the heat dissipation efficiency of the cooling gas on the simulated sidewall 4 while ensuring uniform heat dissipation, effectively mitigating the material performance degradation, thermal oxidation aging, and localized melting deformation problems caused by high temperatures on the simulated sidewall 4.

[0087] In the embodiments of this application, the shape and structure of the cooling rib 41 are not subject to many restrictions, as long as the cooling rib 41 can increase the contact area between the simulated sidewall 4 and the cooling gas. For example, the cross-section of the cooling rib 41 can be square, rectangular, or semi-circular.

[0088] To further enhance the cooling effect of the cooling gas on the simulated sidewall 4, in one embodiment of this application, such as Figure 13As shown, the cross-section of the cooling rib 41 can be hexagonal. It is important to note that if the cross-section of the cooling rib 41 is hexagonal, the hexagonal structure significantly increases the contact area between the cooling gas and the simulated sidewall 4, extending the heat exchange path and enhancing convective heat transfer efficiency. Simultaneously, the angular structure of the hexagon can break the laminar flow of the cooling airflow, promoting turbulence generation, increasing the local heat transfer coefficient, and allowing the cooling gas to more effectively remove heat from the simulated sidewall 4, further mitigating the material performance degradation problem caused by high temperatures. In other words, it further enhances the cooling effect of the cooling gas on the simulated sidewall 4.

[0089] In one embodiment of this application, the distribution of the cooling ribs 41 is not subject to excessive restrictions, as long as the cooling ribs 41 do not disrupt the flow stability of the airflow in the cooling cavity 71. For example, the extending direction of the cooling ribs 41 may intersect with the first direction; or, as... Figure 11 As shown, the extending direction of the cooling rib 41 is perpendicular to the first direction (i.e., Figure 11 (direction E in the middle).

[0090] In embodiments where the extending direction of the cooling rib 41 is perpendicular to the first direction and the cross-section of the cooling rib 41 is a regular hexagon, such as Figure 13 As shown, one edge of the regular hexagon in the cooling rib 41 can face the incoming flow direction (i.e., as shown in the diagram). Figure 13 (Direction E shown). In this embodiment, if one edge of the regular hexagon in the cooling rib 41 faces the incoming flow direction, the flat edge of the regular hexagon forms a direct contact with the incoming flow direction. The airflow separation point is closer to the wall, forming a thinner boundary layer and reducing energy loss during airflow. Simultaneously, the symmetrical structure of the regular hexagon allows the airflow to be evenly distributed along the edge of the cooling rib 41, avoiding local airflow accumulation or gaps and ensuring the stability of the flow field within the cooling cavity 71. Furthermore, the design of facing the incoming flow guides the cooling gas to flow closely against the surface of the cooling rib 41, extending the contact time between the airflow and the cooling rib 41 and the simulated sidewall 4. Combined with the larger surface area of ​​the regular hexagon, this enhances convective heat transfer efficiency. This structure also suppresses eddy current generation, preventing heat accumulation in localized areas and further improving the uniformity of cooling in the high-temperature region of the simulated sidewall 4, effectively delaying material thermal decay and ablation problems.

[0091] To further enhance the cooling effect of the cooling gas on the simulated sidewall 4, in one embodiment of this application, such as Figure 12 As shown, each cooling rib 41 is provided with multiple cooling holes 42. Figure 13 As shown, the angle between the axis of each cooling hole 42 and the outer wall surface of the simulated sidewall 4 (i.e., as shown) Figure 13The included angle N shown is greater than or equal to 25° and less than or equal to 45°. The distance between the front end of each cooling hole 42 and the outer wall of the simulated sidewall 4 is greater than the distance between the rear end of the cooling hole 42 and the outer wall of the simulated sidewall 4.

[0092] In this embodiment, the distance between the front end of the cooling hole 42 and the outer wall surface of the simulated sidewall 4 refers to the distance from the center point of the front end face of the cooling hole 42 to the outer wall surface of the simulated sidewall 4 (i.e., as shown in the figure). Figure 13 The distance H3 shown. The distance between the rear end of the cooling hole 42 and the outer wall surface of the simulated sidewall 4 refers to the distance from the center point of the rear end face of the cooling hole 42 to the outer wall surface of the simulated sidewall 4 (i.e., as shown). Figure 13 The distance H4 is shown.

[0093] In this embodiment, the included angle N can be any degree value among 25°, 30°, 35°, 40° and 45°, or any degree value between two adjacent degrees mentioned above.

[0094] In this embodiment, the arrangement of each cooling hole 42 creates an inclined impact flow channel (i.e., each cooling hole 42) inside the cooling rib 41, further expanding the contact area between the cooling gas and the simulated sidewall 4. The axis of the cooling hole 42 forms an angle greater than or equal to 25° and less than or equal to 45° with the outer wall surface of the simulated sidewall 4. Combined with the inclined layout where the front end of the cooling hole 42 is farther from the simulated sidewall 4 and the rear end is closer, the cooling gas passing through the cooling hole 42 can form a directional impact on the simulated sidewall 4, directly acting on the high-temperature area of ​​the simulated sidewall 4 to achieve impact cooling. Simultaneously, the impact airflow interacts with the mainstream cooling airflow in the cooling chamber 71 to form a secondary flow, which, in conjunction with the convective heat transfer function of the cooling rib 41, constructs a composite heat exchange system that enhances convection and impact cooling, further improving heat exchange efficiency and more comprehensively removing heat from the simulated sidewall 4. In other words, it further enhances the cooling effect of the cooling gas on the simulated sidewall 4.

[0095] like Figure 15 and Figure 16 As shown, Figure 15 The convective heat transfer coefficient cloud map of the simulated sidewall corresponding to the embodiment that only uses the inlet pipe 61, outlet pipe 62 and cooling sidewall 7 in this application; Figure 16 The convective heat transfer coefficient cloud diagram corresponding to the embodiment that adopts the inlet pipe 61, outlet pipe 62, cooling sidewall 7, and cooling ribs 41 with a regular hexagonal cross-section, and cooling holes 42 with an included angle N of 30° on the cooling ribs 41, is shown. Figure 16 and Figure 15The comparison shows that the embodiments of this application have a significant cooling effect on the simulated sidewall by using cooling ribs 41 with a cross-section of regular hexagon and setting inclined cooling holes 42 on the cooling ribs 41.

[0096] The embodiment of the sidewall structure proposed in this application, by dividing the sidewall into a casing sidewall and a simulated sidewall, and setting an axial first gap and a radial second gap between the casing sidewall and the simulated sidewall, can specifically solve the thermal stress problem caused by uneven temperature distribution in the sidewall structure during the test. During the test, the simulated sidewall directly contacts the high-temperature combustion gas, resulting in a large thermal expansion amplitude. Conversely, the casing sidewall does not directly contact the high-temperature combustion gas, resulting in a small thermal expansion amplitude. The first and second gaps provide buffer space for the differential expansion of the casing sidewall and the simulated sidewall, preventing stress accumulation due to mutual compression, effectively preventing plastic deformation or cracking of the sidewall structure, ensuring the structural reliability of the combustion chamber test piece, and extending its service life.

[0097] Having described the sidewall structure of the combustion chamber test specimen proposed in the embodiments of this application, the following describes an embodiment of a combustion chamber test specimen proposed in this application. Specifically, the combustion chamber test specimen includes the sidewall structure described in any of the embodiments above.

[0098] The embodiment of the combustion chamber test specimen proposed in this application addresses the thermal stress problem caused by uneven temperature distribution in the sidewall structure during testing by dividing the sidewall into a casing sidewall and a simulated sidewall, and setting an axial first gap and a radial second gap between the casing sidewall and the simulated sidewall. During testing, the simulated sidewall directly contacts the high-temperature combustion gas, resulting in a large thermal expansion amplitude. Conversely, the casing sidewall does not directly contact the high-temperature combustion gas, resulting in a smaller thermal expansion amplitude. The first and second gaps provide buffer space for the differential expansion of the casing sidewall and the simulated sidewall, preventing stress accumulation due to mutual compression, effectively preventing plastic deformation or cracking of the sidewall structure, ensuring the structural reliability of the combustion chamber test specimen, and extending its service life.

[0099] Although embodiments of this application have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and variations can be made to these embodiments without departing from the principles and spirit of this application, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A sidewall structure for a combustion chamber test specimen, characterized in that, include: Front connecting flange (1) and rear connecting flange (2); The casing sidewall (3) is disposed between the front connecting flange (1) and the rear connecting flange (2); A simulated sidewall (4) is movably disposed on the casing sidewall (3); and a first gap and a second gap are formed between the casing sidewall (3) and the simulated sidewall (4); the first gap is the gap between the casing sidewall (3) and the simulated sidewall (4) along the axial direction of the combustion chamber test piece; the second gap is the gap between the casing sidewall (3) and the simulated sidewall (4) along the radial direction of the combustion chamber test piece.

2. The sidewall structure of the combustion chamber test specimen according to claim 1, characterized in that, The front end of the casing sidewall (3) is movably inserted into the front connecting flange (1), and a third gap is formed between the casing sidewall (3) and the front connecting flange (1), the third gap being the gap between the casing sidewall (3) and the front connecting flange (1) along the axial direction of the combustion chamber test piece; the rear end of the casing sidewall (3) is fixedly connected to the rear connecting flange (2); and / or, the rear end of the casing sidewall (3) is movably inserted into the rear connecting flange (2), and a fourth gap is formed between the casing sidewall (3) and the rear connecting flange (2), the fourth gap being the gap between the casing sidewall (3) and the rear connecting flange (2) along the axial direction of the combustion chamber test piece; the rear end of the casing sidewall (3) is fixedly connected to the front connecting flange (1).

3. The sidewall structure of the combustion chamber test specimen according to claim 1, characterized in that, The connecting edges of the casing sidewall (3) and the simulated sidewall (4) are stepped, so that the casing sidewall (3) and the simulated sidewall (4) can be connected in an active manner.

4. The sidewall structure of the combustion chamber test specimen according to claim 3, characterized in that, The stepped edge opening of the casing sidewall (3) faces the outside of the combustion chamber test piece; the stepped edge opening of the simulated sidewall (4) faces the inside of the combustion chamber test piece; the sidewall structure also includes a plurality of elastic elements (5), each elastic element (5) is distributed around the circumference of the simulated sidewall (4), and one end of each elastic element (5) is connected to the outer wall surface of the casing sidewall (3), and the other end of each elastic element (5) abuts against the outer wall surface of the simulated sidewall (4).

5. The sidewall structure of the combustion chamber test specimen according to claim 4, characterized in that, The elastic element (5) includes a straight section (51) and a bending elastic section (52) connected in sequence.

6. The sidewall structure of the combustion chamber test specimen according to claim 1, characterized in that, The first gap is larger than the second gap; the ratio of the first gap to the second gap is equal to the ratio of the length to the width of the simulated sidewall (4).

7. The sidewall structure of the combustion chamber test specimen according to any one of claims 1 to 6, characterized in that, The sidewall structure also includes: A cooling sidewall (7) is disposed on the outer wall surface of the simulated sidewall (4); a cooling cavity (71) is formed between the cooling sidewall (7) and the simulated sidewall (4); the cooling cavity (71) covers the high-temperature area of ​​the simulated sidewall (4) during the test; The air inlet pipe (61) and the air outlet pipe (62) are both located on the cooling sidewall (7), and the air inlet pipe (61) and the air outlet pipe (62) are both connected to the cooling chamber (71).

8. The sidewall structure of the combustion chamber test specimen according to claim 7, characterized in that, The cooling cavity (71) is also provided with a plurality of cooling ribs (41); each cooling rib (41) is provided on the outer wall surface of the simulated side wall (4), and each cooling rib (41) is distributed sequentially along a first direction; the first direction is parallel to the flow direction of the airflow in the cooling cavity (71).

9. The sidewall structure of the combustion chamber test specimen according to claim 8, characterized in that, Each cooling rib (41) extends perpendicular to the first direction, and each cooling rib (41) has a hexagonal cross-section.

10. A combustion chamber test specimen, characterized in that, Includes the sidewall structure as described in any one of claims 1 to 9.

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