A labyrinth seal robustness test platform in a non-rigid rotor system

Abstract

The application discloses a labyrinth seal robustness test platform in a non-rigid rotor system and relates to the technical field of gas turbine engines. The platform comprises an axial displacement mechanism, a variable stiffness system and a labyrinth element test section. The variable stiffness system is installed on the top of the axial displacement mechanism, and the labyrinth element test section is connected with the axial displacement mechanism through a main shaft connecting plate. The axial displacement mechanism is used for realizing axial position adjustment and axial displacement deviation injection. The variable stiffness system is used for realizing continuous variable stiffness adjustment. The test section is used for developing principle tests of different labyrinth configurations. The injection of labyrinth gap deviation is realized by installing electric heating sheets on the surface of the labyrinth disc. The test system composed of the three parts enables the test platform to study the influence of the axial displacement-radial gap-pneumatic force coupling on the labyrinth seal performance in the non-rigid rotor system and the response law of the seal system to the axial displacement or the radial gap deviation.

Description

Technical Field

[0001] This invention relates to the field of gas turbine engine technology, and more specifically to a test platform for the robustness of the tooth seal in a non-rigid rotor system. Background Technology

[0002] Labyrinth seals (also known as labyrinth seals) are a typical rotary-static seal structure. Due to their simple structure, reliability, and high-efficiency sealing performance, they are widely used in the secondary air system of gas turbine engines, where they perform multiple functions such as bearing cavity lubricating oil sealing, rotor axial force adjustment, and rim gas sealing.

[0003] As a complex system composed of multiple components, a gas turbine engine is characterized by its "strong integration." During operation, the rotor system is subjected to both thermal loads (thermal stress) and mechanical loads (centrifugal force, aerodynamic force, etc.), resulting in radial centrifugal deformation, thermal deformation, and axial tensile deformation. The grate seal, as part of the rotor system, is affected by these changes. Radial centrifugal and thermal deformation alter the grate seal clearance, while axial tensile deformation alters the relative axial position between the grate disc and the seal ring. These changes in seal clearance and relative axial position affect the grate seal performance, which in turn impacts various functions of the air system, such as sealing and rotor axial force adjustment.

[0004] However, current experimental studies on the sealing characteristics of grates typically focus only on the grating element itself, optimizing its sealing performance under the condition that the inlet and outlet boundaries of the grates remain unchanged. These studies primarily focus on the sealing performance of the grates under single operating conditions and single gap / axial displacement scenarios. They fail to consider the actual performance of the grating element in the system environment, nor the impact of gap or axial displacement changes on the grating sealing performance and system response. This may lead to the grating sealing flow exhibiting strong sensitivity to gap or axial displacement changes in the system environment (poor robustness of the grating seal), resulting in the rotor axial force being sensitive to gap or axial displacement changes.

[0005] Most existing test bench designs or test methods for toothed seals are based on rigid or near-rigid assumptions, which cannot simulate the axial displacement in a real rotor system and its impact on the performance of the toothed seal. At the same time, they can only study the effect of single factors such as axial displacement or radial clearance on the performance of the toothed seal, and cannot conduct experimental research on the impact of coupled effects of axial displacement, radial clearance, and aerodynamic forces on the performance of the toothed seal. They also cannot evaluate the robustness of the toothed seal during operation. Summary of the Invention

[0006] The main objective of this invention is to provide a test platform for the robustness of the tooth sealing in a non-rigid rotor system, so as to overcome the problems existing in the prior art.

[0007] To solve the above-mentioned technical problems, the present invention adopts the following technical solution:

[0008] A test platform for the robustness of the tooth sealing in a non-rigid rotor system includes an axial displacement mechanism, a variable stiffness system, and a tooth element test section, wherein the tooth element test section is connected to the axial displacement mechanism via a main shaft connecting mounting plate.

[0009] The axial displacement mechanism is used to adjust the axial position of the rotor system and to simulate the axial displacement of the rotor system caused by aerodynamic forces. The variable stiffness system utilizes the compressibility of gas to achieve continuous adjustment of the stiffness of the gas spring, thereby achieving continuous adjustment of the axial stiffness of the entire rotor system. The toothed element test section is used to conduct tests on toothed discs with different tooth profiles.

[0010] Furthermore, the axial displacement mechanism includes a fixed base, a mounting base, a servo motor, a reducer, a coupling, a moving base, a force sensor, a lead screw and nut connector, a lead screw and nut, a ball screw, a bearing support, a linear guide, a first slider group, and a second slider group.

[0011] The mounting base is fixedly mounted on the top of the fixed base. The servo motor is fixedly mounted on the top of the mounting base. The reducer and the coupling are sequentially arranged at the output end of the servo motor. One end of the ball screw is mounted on the output end of the coupling, and the other end is rotatably connected to the bearing support. The bearing support is fixedly mounted on the top of the fixed base. The screw nut is threadedly connected to the ball screw. The screw nut connector is mounted on the end of the screw nut. The moving base is fixedly mounted on the top of the screw nut connector. The linear guide is fixedly mounted on the top of the mounting base. The first slider group and the second slider group are both slidably connected to the linear guide. The second slider group is connected to the bottom of the moving base. The first slider group is connected to both sides of the bottom of the variable stiffness system. The two ends of the variable stiffness system are connected to the top of the moving base through mounting flanges. The toothed element test section is mounted on the top of the mounting base.

[0012] Furthermore, a bearing mounting seat is sleeved on the outer side of the middle part of the ball screw, a first rolling bearing is installed between the ball screw and the bearing mounting seat, and a second rolling bearing is installed between the end of the ball screw and the bearing support seat.

[0013] Furthermore, for the axial position adjustment of the rotor system, the servo motor outputs power to the ball screw through the reducer and the coupling. The rotation of the ball screw drives the screw nut to move axially. The screw nut drives the moving base plate to move axially through the screw nut connector. The moving base plate slides on the linear guide rail through the second slider group, thereby changing the axial position of the variable stiffness system and adjusting the axial position of the test section rotor.

[0014] Furthermore, the variable stiffness system includes a gas spring, a first mounting flange, a second mounting flange, a gas filling and discharging pipe, a pressure gauge, reinforcing ribs, a main shaft connection mounting plate, a slider mounting plate, and a force sensor mounting plate.

[0015] The gas spring is connected to one end of the gas charging / discharging pipe, and the other end of the gas charging / discharging pipe is connected to the pressure gauge. The first mounting flange and the second mounting flange are located at both ends of the gas spring. The main shaft connecting mounting plate is located on the outside of the first mounting flange, and the force sensor mounting plate is located on the outside of the second mounting flange. The force sensor is mounted on the inner wall of the force sensor mounting plate. The two ends of the reinforcing rib are connected between the main shaft connecting mounting plate and the force sensor mounting plate, and the two reinforcing ribs are located on both sides of the gas spring. The slider mounting plate is installed at the bottom of the reinforcing rib, the main shaft connecting mounting plate, and the force sensor mounting plate. The first slider assembly is installed at the bottom of the slider mounting plate.

[0016] Furthermore, for the axial displacement change of the rotor system caused by aerodynamic force, the aerodynamic axial force of the test section of the toothed element is transmitted to the gas spring through the main shaft connecting mounting plate, reinforcing rib and force sensor mounting plate, thereby simulating the axial displacement change of the rotor system under the action of aerodynamic force.

[0017] Furthermore, the test section of the grating element includes a main mounting shaft, a linear bearing, a shaft plug seal, a linear bearing cover, a plug seal pressure plate, an electric heating element, an air intake chamber, a radial displacement sensor, a sealing ring, a temperature control annular cavity, an end cover, a grating disc, an axial displacement sensor, an exhaust system interface, a sensor lead hole, and a lock nut.

[0018] The air intake chamber is mounted on the mounting base plate, the sealing ring is mounted on the side of the air intake chamber, the grating disc is located inside the sealing ring, the end cap is mounted on the side of the sealing ring away from the air intake chamber, one end of the main mounting shaft is mounted on the side of the main shaft connecting mounting plate, and the other end passes through the air intake chamber, the grating disc, and the end cap. Linear bearings are provided between the main mounting shaft and the air intake chamber, and between the main mounting shaft and the end cap. The end of the linear bearing is provided with a shaft plug seal, a linear bearing cover, and a plug seal pressure plate. A grating disc mounting seat is provided between the main mounting shaft and the grating disc and is fixed with a lock nut.

[0019] The electric heating element is disposed on the surface of the toothed disc, an annular air intake chamber is disposed inside the air intake chamber, the radial displacement sensor is disposed on the outer wall of the sealing ring, the temperature control annular cavity is disposed inside the sealing ring, the axial displacement sensor is disposed on the inner side wall of the end cover, the exhaust system interface is disposed on the outer side wall of the end cover, and the sensor lead hole is disposed on the main mounting shaft.

[0020] Compared with the prior art, the present invention has the following beneficial effects:

[0021] The test bench of this invention breaks through the rigid or near-rigid assumptions in traditional test design. It simulates the stiffness of the rotor system through a designed variable stiffness system and has continuous adjustment capability.

[0022] Secondly, the combination of the axial displacement mechanism and the variable stiffness system can not only enable the tester to actively adjust the axial displacement, i.e., adjust the initial axial position (operation performed before the test) and inject the axial displacement deviation (operation performed during the test), but can also be used to simulate the axial displacement change of the rotor system caused by aerodynamic forces.

[0023] Ultimately, the axial position adjustment and axial displacement deviation injection were achieved through the axial displacement mechanism, the continuous variable stiffness adjustment was achieved through the variable stiffness system, and the test section for the toothed element was used to conduct toothed element tests. It also has the ability to inject radial clearance deviation into the toothed element. The test system composed of these three components enables the test bench to conduct research on the impact of axial displacement-radial clearance-aerodynamic coupling on the toothed sealing performance in a non-rigid rotor system, as well as the response law of the sealing system to axial displacement or radial clearance deviation. This system can well support the stability / robustness design of toothed sealing elements. Attached Figure Description

[0024] Figure 1 This is the overall assembly drawing of the test platform of the present invention.

[0025] Figure 2 This is a three-dimensional structural diagram of the axial displacement mechanism and variable stiffness system of the present invention.

[0026] Figure 3 This is a side view of the axial displacement mechanism and variable stiffness system of the present invention.

[0027] Figure 4 This is a cross-sectional view of the axial displacement mechanism and variable stiffness system of the present invention at point AA.

[0028] Figure 5 This is a schematic diagram of the movable substrate structure of the present invention.

[0029] Figure 6 This is a front view of the lead screw and nut connector of the present invention.

[0030] Figure 7 This is a top view of the lead screw and nut connector of the present invention.

[0031] Figure 8 This is a schematic diagram of the variable stiffness system components of the present invention.

[0032] Figure 9 This is a simplified diagram of the force direction of the variable stiffness system and connection points of the present invention.

[0033] Figure 10 This is an assembly diagram of the test section of the toothed component of the present invention.

[0034] Figure 11 This is a front view of the test section of the toothed element of the present invention.

[0035] Figure 12 This is a cross-sectional view of the test section BB of the toothed element of the present invention.

[0036] Among them, 1-axial displacement mechanism, 101-fixed base, 102-mounting base plate, 103-servo motor, 104-reducer, 105-coupling, 106-moving base plate, 107-first rolling bearing, 108-force sensor, 109-screw nut connector, 110-screw nut, 111-ball screw, 112-bearing support seat, 113-first rolling bearing, 114-linear guide rail, 115-first slider group, 116-second slider group, 2-variable stiffness system, 201-gas spring, 202-first mounting flange, 203-second mounting flange, 204-gas charging and discharging pipe, 205-pressure gauge, 206-reinforcing rib, 207-spindle connection mounting plate, 208-slider mounting plate, 20 9-Force sensor mounting plate, 3-Grate element test section, 301-Main mounting shaft, 302-Linear bearing, 303-Shaft plug seal, 304-Linear bearing cover, 305-Plug seal pressure plate, 306-Electric heating element, 307-Inlet chamber, 308-Radial displacement sensor, 309-Sealing ring, 310-Sealing ring temperature control annular cavity, 311-End cover, 312-Grate disc, 313-Axial displacement sensor, 314-Exhaust system interface, 315-Sensor lead hole, 316-Locking nut, 317-Grate disc mounting base, 318-Grate disc mounting accessory, 1061-First bolt hole, 1062-Second bolt hole, 1063-Third bolt hole, 1091-Fourth bolt hole, 1092-Fifth bolt hole. Detailed Implementation

[0037] The technical solution of the present invention will be further described below with reference to the accompanying drawings and embodiments.

[0038] Combination Figures 1 to 12 This embodiment provides a test platform for the robustness of the tooth sealing in a non-rigid rotor system, including an axial displacement mechanism 1, a variable stiffness system 2, and a tooth element test section 3. The variable stiffness system 2 is installed on the top of the axial displacement mechanism 1, and the tooth element test section 3 is connected to the axial displacement mechanism 1 through a main shaft connecting mounting plate 207.

[0039] In this embodiment, the axial displacement mechanism 1 includes a fixed base 101, a mounting base 102, a servo motor 103, a reducer 104, a coupling 105, a moving base 106, a force sensor 108, a lead screw and nut connector 109, a lead screw and nut 110, a ball screw 111, a bearing support 112, a linear guide rail 114, a first slider group 115, and a second slider group 116.

[0040] The mounting base 102 is fixedly mounted on the top of the fixed base 101. The servo motor 103 is fixedly mounted on the top of the mounting base 102. The reducer 104 and the coupling 105 are sequentially arranged at the output end of the servo motor 103. One end of the ball screw 111 is mounted on the output end of the coupling 105, and the other end is rotatably connected to the bearing support 112. The bearing support 112 is fixedly mounted on the top of the fixed base 101. The screw nut 110 is threadedly connected to the ball screw 111. The screw nut connector 109 is mounted on the screw nut 111. At the end of 0, the movable base plate 106 is fixedly installed on the top of the lead screw nut connector 109, the linear guide rail 114 is fixedly installed on the top of the mounting base plate 102, the first slider group 115 and the second slider group 116 are both slidably connected to the linear guide rail 114, the second slider group 116 is connected to the bottom of the movable base plate 106, the first slider group 115 is connected to the bottom two sides of the variable stiffness system 2, the two ends of the variable stiffness system 2 are connected to the top of the movable base plate 106 through mounting flanges, and the toothed element test section 3 is installed on the top of the mounting base plate 102.

[0041] Preferably, a bearing mounting seat is sleeved on the outer side of the middle part of the ball screw 111, a first rolling bearing 107 is installed between the ball screw 111 and the bearing mounting seat, and a second rolling bearing 113 is installed between the end of the ball screw 111 and the bearing support seat 112.

[0042] In this embodiment, the variable stiffness system 2 includes a gas spring 201, a first mounting flange 202, a second mounting flange 203, a gas filling and discharging pipe 204, a pressure gauge 205, a reinforcing rib 206, a spindle connection mounting plate 207, a slider mounting plate 208, and a force sensor mounting plate 209.

[0043] The gas spring 201 is connected to one end of the gas charging / discharging pipe 204, and the other end of the gas charging / discharging pipe 204 is connected to the pressure gauge 205. The first mounting flange 202 and the second mounting flange 203 are disposed at both ends of the gas spring 201. The main shaft connecting mounting plate 207 is disposed on the outside of the first mounting flange 202. The force sensor mounting plate 209 is disposed on the outside of the second mounting flange 203. The force sensor 108 is mounted on the inner wall of the force sensor mounting plate 209. The two ends of the reinforcing rib 206 are connected between the main shaft connecting mounting plate 207 and the force sensor mounting plate 209, and the two reinforcing ribs 206 are respectively located on both sides of the gas spring 201. The slider mounting plate 208 is mounted at the bottom of the reinforcing rib 206, the main shaft connecting mounting plate 207 and the force sensor mounting plate 209. The first slider assembly 115 is mounted at the bottom of the slider mounting plate 208.

[0044] In this embodiment, the gas spring 201 is connected to the first mounting flange 202 by bolts. The first mounting flange 202 and the second mounting flange 203 are connected to the first bolt hole 1061 by four bolts. There are three second bolt holes 1062, which are connected to the three fifth bolt holes 1092 on the lead screw nut connector 109 by bolts. The third bolt hole 1063 is used to fix the movable base plate 106 to the slider on the linear guide rail 114. Each slider corresponds to four third bolt holes, and there are a total of four sliders, corresponding to 16 third bolt holes. The fourth bolt hole 1091 is connected to the corresponding hole on the lead screw nut 110 by bolts.

[0045] The movable base plate 106 is connected to the lead screw nut connector 109, and then the lead screw nut connector 109 is connected to the lead screw nut 110, thus realizing the connection of these three parts. The gas spring 201 is fixed on the movable base plate 106 through the first mounting flange 202 and the second mounting flange 203.

[0046] In this embodiment, the test section 3 of the toothed element includes a main mounting shaft 301, a linear bearing 302, a shaft plug seal 303, a linear bearing cover 304, a plug seal pressure plate 305, an electric heating element 306, an air intake chamber 307, a radial displacement sensor 308, a sealing ring 309, a temperature control annular cavity 310, an end cover 311, a toothed disc 312, an axial displacement sensor 313, an exhaust system interface 314, a sensor lead hole 315, a locking nut 316, and a toothed disc mounting base 317.

[0047] The air intake chamber 307 is mounted on the mounting base plate 102. The sealing ring 309 is mounted on the side of the air intake chamber 307. The toothed disc 312 is located inside the sealing ring 309. The end cap 311 is mounted on the side of the sealing ring 309 away from the air intake chamber 307. One end of the main mounting shaft 301 is mounted on the side of the main shaft connecting mounting plate 207, and the other end passes through the air intake chamber 307, the toothed disc 312, and the end cap 311. Linear bearings 302 are provided between the main mounting shaft 301 and the air intake chamber 307, and between the main mounting shaft 301 and the end cap 311. The end of the linear bearing 302 is provided with a shaft plug seal 303, a linear bearing cover 304, and a plug seal pressure plate 305. A toothed disc mounting seat is provided between the main mounting shaft 301 and the toothed disc 312 and is fixed with a lock nut 316.

[0048] The electric heating element 306 is disposed on the surface of the toothed disc 312. The air intake chamber 307 is provided with an annular air intake chamber. The radial displacement sensor 308 is disposed on the outer wall of the sealing ring 309. The temperature control annular cavity 310 is disposed inside the sealing ring 309. The axial displacement sensor 313 is disposed on the inner side wall of the end cover 311. The exhaust system interface 314 is disposed on the outer side wall of the end cover 311. The sensor lead hole 315 is disposed on the main mounting shaft 301.

[0049] In this embodiment, the axial displacement mechanism 1 is a mechanical mechanism for adjusting the axial position of the rotor system and simulating the axial displacement of the rotor system caused by aerodynamic forces. During the test, the former, axial position adjustment / axial displacement, needs to be achieved through the subjective will of the tester, that is, the magnitude of the axial position adjustment is determined by the tester. The adjustment of the axial position includes both the adjustment of the initial axial position and the axial displacement applied during the test. This change in axial displacement is referred to as axial displacement deviation injection. The latter, the axial displacement generated, is the capability or attribute of the test system itself, and the magnitude of the axial displacement is determined by the test conditions.

[0050] Specifically, for adjusting the axial position of the rotor system, the servo motor 103 outputs power to the ball screw 111 via the reducer 104 and the coupling 105. The rotation of the ball screw 111 drives the screw nut 110 to move axially. The screw nut 110 drives the moving base plate 106 to move axially via the screw nut connector 109. The moving base plate 106 slides on the linear guide rail 114 via the second slider group 116, thereby changing the axial position of the variable stiffness system 2. Figure 4 As shown, the position control of the servo motor 103 is used to convert the rotary motion into linear motion, thereby realizing the axial position control of the load.

[0051] For the axial displacement change of the rotor system caused by aerodynamic force, the aerodynamic axial force of the test section 3 of the toothed element is transmitted to the gas spring 201 through the main shaft connecting mounting plate 207, the reinforcing rib 206, and the force sensor mounting plate 209. Under the action of the force, the piston rod of the gas spring (201) is compressed, thereby generating axial displacement. The main shaft connecting mounting plate 207, the reinforcing rib 206, and the slider mounting plate 208 move axially on the linear guide rail 114 along with the first slider group 115, thereby simulating the axial displacement change of the rotor system under the action of aerodynamic force. The force directions of each component are as follows: Figure 9 As shown. The slider assembly 115 is mounted on the linear guide rail 114. The reinforcing rib 206, the spindle connection mounting plate 207, and the force sensor mounting plate 209 are connected to the slider assembly 115 through the slider mounting plate 208.

[0052] In this embodiment, the variable stiffness system 2 is a subsystem capable of continuously adjusting axial stiffness. The working medium of the gas spring 201 includes, but is not limited to, compressible gases such as air and nitrogen. Figure 8 As shown, its purpose is to utilize the compressibility of gas to achieve continuous adjustment of the stiffness of the gas spring, thereby realizing the stiffness adjustment of the entire rotor system.

[0053] In this embodiment, the toothed element test section 3 is a subsystem that can conduct tests on toothed discs with different tooth structures.

[0054] Specifically, the gap deviation is injected through thermal deformation, since the gap is the fitting clearance between the sealing ring and the grate plate. Therefore, in this experiment, circulating cooling water is introduced into the annular cavity inside the sealing ring to ensure that the sealing ring is in a constant temperature environment and does not produce thermal deformation or minimizes thermal deformation as much as possible. The radial deformation of the grate plate is controlled by hot air heating or by arranging electric heating elements on the surface of the grate plate. That is, the gap deviation comes entirely from the deformation of the grate plate.

[0055] In addition, the test section adopts a modular design, and different test requirements can be met by replacing the sealing ring 309 with a different structure or the toothed disc 312 with a different structure.

[0056] Specifically, the test bench is first divided into three parts (modules): an axial displacement mechanism, a variable stiffness system, and a test section for the toothed components. Each part is connected by standard bolts, allowing for individual debugging and installation of each module by connecting or disconnecting the bolts. Secondly, the test section allows for different toothed tests by replacing the sealing ring and toothed disc with different configurations. The main design requirements for the sealing ring are the same as in this test; the specific differences lie in the structure of the inner ring step, such as no step or other types of steps. The design requirements for the toothed disc are primarily for compatibility with the toothed disc mounting base and accessories; replacement is possible as long as the interfaces are identical.

[0057] To reduce the sensitivity of the grate sealing performance to deviations in parameters such as radial clearance and axial displacement, and to improve the robustness of the grate sealing, this embodiment proposes a test platform for the robustness of the grate sealing in a non-rigid rotor system. This test platform has the ability to actively adjust the relative position of the grate disk and the sealing ring, and the axial displacement can change with the aerodynamic force during the test. At the same time, the test platform has the ability to inject grate sealing clearance deviations, and can carry out steady-state tests under different boundary conditions, different axial positions, and different sealing clearances for different grate configurations, as well as transient response tests of the system when there are axial displacement deviations and radial clearance deviations.

[0058] The above description is merely a preferred embodiment of the present invention and does not constitute any limitation on the technical scope of the present invention. Therefore, any minor modifications, equivalent changes and alterations made to the above embodiments based on the technical essence of the present invention shall still fall within the scope of the technical solution of the present invention.

Claims

1. A test platform for the robustness of tooth sealing in a non-rigid rotor system, characterized in that, It includes an axial displacement mechanism (1), a variable stiffness system (2) and a toothed element test section (3). The variable stiffness system (2) is installed on the top of the axial displacement mechanism (1), and the toothed element test section (3) is connected to the spindle connection mounting plate (207) in the variable stiffness system (2). The axial displacement mechanism (1) is used to adjust the axial position of the rotor system and to simulate the axial displacement of the rotor system caused by aerodynamic force. The variable stiffness system (2) includes a gas spring (201) and a main shaft connecting mounting plate (207). The variable stiffness system (2) utilizes the compressibility of gas to achieve continuous adjustment of the stiffness of the gas spring, thereby achieving continuous adjustment of the axial stiffness of the entire rotor system. The toothed element test section (3) is used to conduct tests on toothed discs with different tooth profiles.

2. The test platform for the robustness of the tooth seal in a non-rigid rotor system as described in claim 1, characterized in that, The axial displacement mechanism (1) includes a fixed base (101), a mounting base plate (102), a servo motor (103), a reducer (104), a coupling (105), a moving base plate (106), a force sensor (108), a lead screw and nut connector (109), a lead screw and nut (110), a ball screw (111), a bearing support (112), a linear guide rail (114), a first slider group (115), and a second slider group (116). The mounting base (102) is fixedly mounted on the top of the fixed base (101), the servo motor (103) is fixedly mounted on the top of the mounting base (102), the reducer (104) and the coupling (105) are sequentially arranged at the output end of the servo motor (103), one end of the ball screw (111) is mounted on the output end of the coupling (105), and the other end is rotatably connected to the bearing support (112), the bearing support (112) is fixedly mounted on the top of the fixed base (101), the screw nut (110) is threadedly connected to the ball screw (111), and the screw nut connector (109) is mounted on the screw nut (111). At the end of 0), the movable base plate (106) is fixedly installed on the top of the lead screw nut connector (109), the linear guide rail (114) is fixedly installed on the top of the mounting base plate (102), the first slider group (115) and the second slider group (116) are slidably connected to the linear guide rail (114), the second slider group (116) is connected to the bottom of the movable base plate (106), the first slider group (115) is connected to the bottom two sides of the variable stiffness system (2), the two ends of the variable stiffness system (2) are connected to the top of the movable base plate (106) through the mounting flange, and the toothed element test section (3) is installed on the top of the mounting base plate (102).

3. The test platform for the robustness of the tooth seal in a non-rigid rotor system as described in claim 2, characterized in that, A bearing mounting seat is sleeved on the outer side of the middle part of the ball screw (111), a first rolling bearing (107) is installed between the ball screw (111) and the bearing mounting seat, and a second rolling bearing (113) is installed between the end of the ball screw (111) and the bearing support seat (112).

4. The test platform for the robustness of the tooth seal in a non-rigid rotor system as described in claim 2, characterized in that, For the axial position adjustment of the rotor system, the servo motor (103) outputs power to the ball screw (111) through the reducer (104) and the coupling (105). The rotation of the ball screw (111) drives the screw nut (110) to move axially. The screw nut (110) drives the moving base plate (106) to move axially through the screw nut connector (109). The moving base plate (106) slides on the linear guide rail (114) through the second slider group (116), thereby changing the axial position of the variable stiffness system (2) and adjusting the axial position of the test section rotor.

5. The test platform for the robustness of the tooth seal in a non-rigid rotor system as described in claim 2, characterized in that, The variable stiffness system (2) includes a gas spring (201), a first mounting flange (202), a second mounting flange (203), a gas charging and discharging pipe (204), a pressure gauge (205), a reinforcing rib (206), a spindle connection mounting plate (207), a slider mounting plate (208), and a force sensor mounting plate (209); The gas spring (201) is connected to one end of the gas charging / discharging pipe (204), and the other end of the gas charging / discharging pipe (204) is connected to the pressure gauge (205). The first mounting flange (202) and the second mounting flange (203) are located at both ends of the gas spring (201). The main shaft connecting mounting plate (207) is located on the outside of the first mounting flange (202), and the force sensor mounting plate (209) is located on the outside of the second mounting flange (203). The force sensor (108) is mounted on... On the inner wall of the force sensor mounting plate (209), the two ends of the reinforcing rib (206) are connected between the main shaft connecting mounting plate (207) and the force sensor mounting plate (209), and the two reinforcing ribs (206) are respectively located on both sides of the gas spring (201). The slider mounting plate (208) is installed at the bottom of the reinforcing rib (206), the main shaft connecting mounting plate (207) and the force sensor mounting plate (209), and the first slider group (115) is installed at the bottom of the slider mounting plate (208).

6. The test platform for the robustness of the tooth seal in a non-rigid rotor system as described in claim 5, characterized in that, For the axial displacement change of the rotor system caused by aerodynamic force, the aerodynamic axial force of the test section (3) of the toothed element is transmitted to the gas spring (201) through the main shaft connecting mounting plate (207), the reinforcing rib (206) and the force sensor mounting plate (209). Under the action of the force, the piston rod of the gas spring (201) is compressed, thereby generating axial displacement. The mounting plate (207), the reinforcing rib (206) and the slider mounting plate (208) move axially on the linear guide rail (114) along with the first slider group (115), thereby simulating the axial displacement and the change of axial displacement generated by the rotor system under the action of aerodynamic force.

7. The test platform for the robustness of the tooth seal in a non-rigid rotor system as described in claim 2, characterized in that, The test section (3) of the toothed element includes a main mounting shaft (301), a linear bearing (302), a shaft plug seal (303), a linear bearing cover (304), a plug seal pressure plate (305), an electric heating element (306), an air intake chamber (307), a radial displacement sensor (308), a sealing ring (309), a temperature control annular cavity (310), an end cover (311), a toothed disc (312), an axial displacement sensor (313), an exhaust system interface (314), a sensor lead hole (315), a lock nut (316), a toothed disc mounting base (317), and a toothed disc accessory (318). The air intake chamber (307) is mounted on the mounting base plate (102), the sealing ring (309) is mounted on the side of the air intake chamber (307), the grate plate (312) is located inside the sealing ring (309), the end cap (311) is mounted on the side of the sealing ring (309) away from the air intake chamber (307), one end of the main mounting shaft (301) is mounted on the side of the main shaft connecting mounting plate (207), and the other end passes through the air intake chamber (307) and the grate plate. Linear bearings (302) are provided between the gear disc (312) and the end cover (311), between the main mounting shaft (301) and the air intake chamber (307), and between the main mounting shaft (301) and the end cover (311). The end of the linear bearing (302) is provided with a shaft plug seal (303), a linear bearing cover (304), and a plug seal pressure plate (305). The main mounting shaft (301) and the gear disc (312) are fixed by a lock nut (316). The electric heating element (306) is disposed on the surface of the toothed disc (312), the air intake chamber (307) is disposed inside the test section (3) of the toothed element, the radial displacement sensor (308) is disposed on the outer wall of the sealing ring (309), the temperature control annular cavity (310) is disposed inside the sealing ring (309), the axial displacement sensor (313) is disposed on the inner side wall of the end cover (311), the exhaust system interface (314) is disposed on the outer side wall of the end cover (311), and the sensor lead hole (315) is disposed on the main mounting shaft (301).

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