Rigidity measuring device for squeeze film damper of gas turbine

Abstract

The invention discloses a gas turbine squeeze film damper rigidity measuring device, and relates to the technical field of performance testing of gas turbine rotor system matching parts. The method solves the problems that the measurement precision is restricted by the frequency measurement accuracy in the existing indirect measurement method for speculating the stiffness of the squeeze film damper by measuring the vibration frequency, and errors exist between the obtained comprehensive stiffness and the actually required stiffness of the rotor bearing position. A supporting tool fixes an extrusion oil film damper, a loading tool simulates the assembly relation between a rotor bearing and the extrusion oil film damper, one end of a lever is hinged to a hinge support, the other end of the lever bears the acting force of a probe of a loading sliding platform, and a loading guide rail restrains the movement direction of the loading sliding platform. The displacement measurement module carries out displacement detection corresponding to the bearing installation position. According to the invention, load amplification is realized through the lever principle, the actual rigidity of the squeeze film damper can be accurately obtained by adopting a direct loading and direct displacement measurement mode, and the installation and centering precision of a rotor is guaranteed.

Description

Technical Field

[0001] This invention relates to the field of performance testing technology for components of a gas turbine rotor system, specifically to a device for measuring the stiffness of a gas turbine squeeze film damper. Background Technology

[0002] The squeeze film damper is a component in a gas turbine that connects the casing and rotor bearings, playing a role in improving the vibration performance of the rotor system and the overall stability of the machine. Before installation, the squeeze film damper needs to undergo static bending stiffness measurement. Based on this, the upward offset of the squeeze film damper during installation is calculated to ensure rotor alignment after installation. Existing methods for measuring the stiffness of squeeze film dampers mostly involve measuring the vibration frequency to infer the stiffness, which is an indirect measurement method. The accuracy of this method is limited by the accuracy of the frequency measurement, and the stiffness obtained through vibration testing is the overall stiffness of the squeeze film damper, which has a certain error compared to the stiffness at the actual rotor bearing position. Summary of the Invention

[0003] The purpose of this invention is to solve the problems of existing indirect measurement methods that infer the stiffness of extrusion film dampers by measuring vibration frequency, where the measurement accuracy is limited by the accuracy of frequency measurement and there is an error between the obtained comprehensive stiffness and the actual stiffness required by the rotor bearing position. Therefore, this invention provides a device for measuring the stiffness of gas turbine extrusion film dampers.

[0004] The technical solution of this invention is:

[0005] A stiffness measuring device for a gas turbine squeeze film damper, the device comprising a test rigid platform 1, a hinged bracket 2, a support fixture 3, a loading fixture 4, a loading guide rail 5, a loading sliding platform 6, a lever 7, a displacement measuring module 8, and a squeeze film damper 9.

[0006] The test rigid platform 1 is arranged horizontally. The top center of the test rigid platform 1 is provided with a vertically arranged support fixture 3. The upper part of the support fixture 3 is equipped with a horizontally arranged extrusion oil film damper 9 along the length direction of the test rigid platform 1. The extrusion oil film damper 9 is embedded with a loading fixture 4. The joint between the loading fixture 4 and the extrusion oil film damper 9 is the bearing installation position. The loading fixture 4 is hinged to the lever 7.

[0007] The left and right sides of the extrusion oil film damper 9 are respectively provided with loading guide rail 5 and hinge bracket 2, which are vertically fixed to the top of the test rigid platform 1. One end of the lever 7 is hinged to the hinge bracket 2, and the other end of the lever 7 is located directly below the loading sliding platform 6. The loading sliding platform 6 can slide freely up and down along the loading guide rail 5, and a vertically arranged probe is provided in the middle of the lower part of the loading sliding platform 6. The probe is in contact with the upper end surface of the lever 7.

[0008] A displacement measurement module 8 is located directly below the extrusion oil film damper 9. The displacement measurement module 8 is installed in the middle of the support fixture 3, and the detection end of the displacement measurement module 8 is set to correspond to the bearing installation position.

[0009] Furthermore, the loading fixture 4 is a circular plate with a thickness consistent with the length of the rotor bearing. A rectangular hole is opened in the middle of the circular plate. The lever 7 is a rod-shaped structure with a rectangular cross-section. The middle part of the lever 7 passes through the rectangular hole of the circular plate and is hinged to the loading fixture 4. The outer edge of the circular plate is fixedly connected to the extrusion oil film damper 9 through an interference fit between the hole and the shaft.

[0010] Furthermore, the loading guide rail 5 includes a guide rail fixing base plate 51 and four L-shaped steel bars 52;

[0011] The guide rail fixing base plate 51 is horizontally arranged and fixedly connected to the top of the test rigid platform 1. Four L-shaped steels 52 perpendicular to the ground are fixedly connected to the top of the guide rail fixing base plate 51. The four L-shaped steels 52 are evenly arranged around the circumference.

[0012] Furthermore, four L-shaped steel bars 52 are arranged in pairs on the front and rear sides of the axis of lever 7, and the free end of lever 7 passes through the L-shaped steel bars 52 on both sides.

[0013] Furthermore, the loading sliding platform 6 includes a platform body 61, a round rod 62, and multiple disc-shaped weights 63;

[0014] The platform body 61 is a square flat plate with a certain thickness. The round rod 62 passes vertically through the upper and lower end faces of the platform body 61 at the center position and is fixedly connected by an interference fit through the shaft hole.

[0015] The portion of the round rod 62 located above the platform body 61 is used to limit the horizontal displacement of the disc-shaped weight 63, while the portion located below the platform body 61 forms a probe that contacts the lever 7.

[0016] Furthermore, a circular hole is opened in the center of the disc-shaped weight 63, and the disc-shaped weight 63 is installed on the circular rod 62, with the center of gravity of the disc-shaped weight 63 coinciding with the center line of the circular rod 62.

[0017] Furthermore, the loading sliding platform 6 also includes a contact wheel 64, which is rotatably mounted on the end of the probe and rolls in engagement with the upper surface of the lever 7.

[0018] Furthermore, the loading sliding platform 6 also includes eight pulley modules, which are arranged perpendicularly to each other at the four corners of the platform body 61.

[0019] The platform body 61 is horizontally set within the rectangular area enclosed by the four L-shaped steels 52 of the loading guide rail 5, and is limited in the horizontal direction by the rolling cooperation of eight pulley modules with the four L-shaped steels 52.

[0020] Furthermore, each pulley module includes a pulley retainer 65 and two pulleys 66;

[0021] The pulley fixing device 65 is an isosceles trapezoidal plate structure, which is arranged perpendicularly to the platform body 61 and is fixedly connected to the platform body 61 through a slot on the side facing the platform body 61.

[0022] The pulley retainer 65 has a vertically arranged wheel groove on the side facing the L-shaped steel 52. Two pulleys 66 are rotatably installed in the wheel groove at intervals and roll in cooperation with the inner side of the corresponding L-shaped steel 52.

[0023] Furthermore, the displacement measurement module 8 uses a non-contact displacement sensor, and the detection end of the non-contact displacement sensor is located directly below the bearing mounting position of the extrusion oil film damper 9.

[0024] Compared with the prior art, the present invention has the following advantages:

[0025] 1. This invention simulates the actual assembly state of the rotor bearing and the damper by using an interference fit between the loading fixture 4 and the bore and shaft of the extrusion oil film damper 9, so that the load is directly applied to the bearing mounting position. At the same time, the displacement measurement module 8 uses a non-contact displacement sensor, with the measurement point directly facing the bearing mounting position of the extrusion oil film damper 9, realizing direct load application and displacement detection at the core stiffness measurement position. This avoids the deviation between the comprehensive stiffness and the actual required stiffness in the existing indirect measurement method, and significantly improves the accuracy of the measurement results.

[0026] 2. This invention utilizes the torque balance principle of lever 7. The disc-shaped weight 63 on the loading sliding platform 6 transmits gravity to the right end of lever 7 through the probe. After being amplified by lever 7, it acts on the loading fixture 4, so that a relatively small weight can meet the loading requirements of squeezing the oil film damper 9 to be close to the installation state. No large loading equipment is required, which reduces the investment cost and operation difficulty of the test equipment.

[0027] 3. The loading guide rail 5 of the present invention is arranged in a ring by four L-shaped steels 52. The loading sliding platform 6 is rolled with the L-shaped steels 52 through the pulley modules at the four corners, which effectively constrains the horizontal displacement and vertical axis rotation of the platform body 61. At the same time, the contact wheel 64 at the end of the probe is rolled with the upper surface of the lever 7, which reduces the influence of contact friction on load transmission, ensures that the lever arm of the lever 7 remains unchanged during the addition and subtraction of weights, and the load transmission is not affected by the deformation of the lever, thus ensuring the accuracy of the load amplification factor.

[0028] 4. The core components of this invention, such as the support fixture 3 and the loading fixture 4, adopt a modular design. The loading fixture 4 can be replaced with a circular plate of corresponding thickness according to different rotor bearing lengths. The support fixture 3 can be adapted to different specifications of extrusion oil film dampers 9. The components are easy to disassemble and assemble, and can quickly complete the testing and switching of different types of dampers, thus expanding the application range of the device.

[0029] 5. The device of the present invention has a reasonable overall component layout and simple structure. The test process can be achieved by simply adding or removing the disc-shaped weights 63 on the loading sliding platform 6. The displacement measurement module 8 directly outputs the detection data, without the need for a complicated frequency measurement and conversion process, which greatly simplifies the test process and reduces the workload and operating threshold of the test personnel. Attached Figure Description

[0030] Figure 1 This is an isometric view of the gas turbine squeeze film damper stiffness measuring device of the present invention;

[0031] Figure 2 This is a front view of the gas turbine squeeze film damper stiffness measuring device of the present invention (in the figure, point A is the lever fixed hinge fulcrum, point B is the force fulcrum of the squeeze film damper, point C is the weight loading fulcrum, L1 is the weight lever arm, L2 is the force lever arm of the squeeze film damper, and L1 / L2 is the ratio of the force on the squeeze film damper to the weight of the weight).

[0032] Figure 3 This is an isometric view of the loading guide rail 5 in the gas turbine squeeze oil film damper stiffness measuring device of the present invention;

[0033] Figure 4 This is a front view of the loading guide rail 5 in the gas turbine squeeze oil film damper stiffness measuring device of the present invention;

[0034] Figure 5 This is a top view of the loading guide rail 5 in the gas turbine squeeze oil film damper stiffness measuring device of the present invention;

[0035] Figure 6 This is a schematic diagram of the installation of the loading guide rail 5, the loading sliding platform 6, and the lever 7 in the gas turbine extrusion oil film damper stiffness measuring device of the present invention.

[0036] In the diagram: 1- Rigid experimental platform; 2- Hinged bracket; 3- Support fixture; 4- Loading fixture; 5- Loading guide rail; 6- Loading sliding platform; 7- Lever; 8- Displacement measurement module; 9- Extrusion oil film damper; 51- Guide rail fixing base plate; 52- L-shaped steel; 61- Platform body; 62- Round rod; 63- Disc-shaped weight; 64- Contact wheel; 65- Pulley fixer; 66- Pulley; A- Lever fixing hinge fulcrum; B- Extrusion oil film damper force fulcrum; C- Weight loading fulcrum; L1- Weight gravity lever arm; L2- Extrusion oil film damper force arm; L1 / L2- Ratio of force on extrusion oil film damper to weight gravity. Detailed Implementation

[0037] Specific implementation method one: Combining Figures 1 to 6 This embodiment describes a gas turbine extrusion film damper stiffness measuring device, which includes a test rigid platform 1, a hinged bracket 2, a support fixture 3, a loading fixture 4, a loading guide rail 5, a loading sliding platform 6, a lever 7, a displacement measuring module 8, and an extrusion film damper 9.

[0038] The test rigid platform 1 is arranged horizontally. The top center of the test rigid platform 1 is provided with a vertically arranged support fixture 3. The upper part of the support fixture 3 is equipped with a horizontally arranged extrusion oil film damper 9 along the length direction of the test rigid platform 1. The extrusion oil film damper 9 is embedded with a loading fixture 4. The joint between the loading fixture 4 and the extrusion oil film damper 9 is the bearing installation position. The loading fixture 4 is hinged to the lever 7.

[0039] The left and right sides of the extrusion oil film damper 9 are respectively provided with loading guide rail 5 and hinge bracket 2, which are vertically fixed to the top of the test rigid platform 1. One end of the lever 7 is hinged to the hinge bracket 2, and the other end of the lever 7 is located directly below the loading sliding platform 6. The loading sliding platform 6 can slide freely up and down along the loading guide rail 5, and a vertically arranged probe is provided in the middle of the lower part of the loading sliding platform 6. The probe is in contact with the upper end surface of the lever 7.

[0040] A displacement measurement module 8 is located directly below the extrusion oil film damper 9. The displacement measurement module 8 is installed in the middle of the support fixture 3, and the detection end of the displacement measurement module 8 is set to correspond to the bearing installation position.

[0041] Specific Implementation Method Two: Combining Figures 1 to 6 In this embodiment, the loading fixture 4 is a circular plate with a thickness consistent with the length of the rotor bearing. A rectangular hole is opened in the middle of the circular plate. The lever 7 is a rod-shaped structure with a rectangular cross-section. The middle part of the lever 7 passes through the rectangular hole of the circular plate and is hinged to the loading fixture 4. The outer edge of the circular plate is fixedly connected to the extrusion oil film damper 9 through an interference fit between the hole and the shaft.

[0042] With this configuration, the thickness of the circular plate of the loading fixture 4 is consistent with the length of the rotor bearing, which can accurately simulate the actual assembly conditions of the rotor bearing and the extrusion oil film damper 9, ensuring that the load application position is consistent with the actual working state. The rectangular hole and the lever 7 with a rectangular cross-section cooperate to achieve a hinge, which not only ensures the effective transmission of force between the lever 7 and the loading fixture 4, but also restricts the relative rotation between the two, avoiding offset during load transmission, and further improving the accuracy of load application. Other components and connection relationships are the same as in specific implementation method one.

[0043] Specific implementation method three: Combining Figures 1 to 6 This embodiment describes the loading guide rail 5, which includes a guide rail fixing base plate 51 and four L-shaped steel bars 52.

[0044] The guide rail fixing base plate 51 is horizontally arranged and fixedly connected to the top of the test rigid platform 1. Four L-shaped steels 52 perpendicular to the ground are fixedly connected to the top of the guide rail fixing base plate 51. The four L-shaped steels 52 are evenly arranged around the circumference.

[0045] With this configuration, four L-shaped steel beams 52 are evenly arranged around the circumference, forming a stable guiding structure. This structure can limit the loading sliding platform 6 from all sides, effectively constraining its horizontal displacement and providing a stable vertical sliding trajectory for the loading sliding platform 6. This ensures the verticality of the load transfer direction and avoids load application deviations caused by platform offset. Other components and connections are the same as in specific implementation methods one or two.

[0046] Specific implementation method four: Combination Figures 1 to 6 To illustrate this embodiment, the four L-shaped steels 52 are arranged in pairs opposite each other on the front and rear sides of the axis of the lever 7, and the free end of the lever 7 passes between the two L-shaped steels 52.

[0047] With this configuration, the free end of lever 7 passes between the two L-shaped steel sections 52. The L-shaped steel sections 52 can act as auxiliary limiters for the free end of lever 7, preventing lever 7 from swinging left and right during the application of force. This further ensures the stability of lever 7 under force and the fixation of the lever arm, ensuring the consistency of the load amplification ratio. Other components and connections are the same as in specific implementation methods one, two, or three.

[0048] Specific Implementation Method Five: Combining Figures 1 to 6 This embodiment describes a loading sliding platform 6 comprising a platform body 61, a round rod 62, and multiple disc-shaped weights 63.

[0049] The platform body 61 is a square flat plate with a certain thickness. The round rod 62 passes vertically through the upper and lower end faces of the platform body 61 at the center position and is fixedly connected by an interference fit through the shaft hole.

[0050] The portion of the round rod 62 located above the platform body 61 is used to limit the horizontal displacement of the disc-shaped weight 63, while the portion located below the platform body 61 forms a probe that contacts the lever 7.

[0051] With this configuration, the round rod 62 vertically penetrates the platform body 61 and is fixed by an interference fit through the shaft hole, resulting in a stable structure and uniform force distribution. The upper part constrains the horizontal position of the disc-shaped weight 63, preventing displacement during weight loading that could cause the center of gravity to shift. The lower part acts as a probe, directly contacting the lever 7 to achieve direct load transfer and ensure that the weight of the weight is accurately converted into the force of the lever 7. Other components and connections are the same as in specific embodiments one, two, three, or four.

[0052] Specific Implementation Method Six: Combination Figures 1 to 6 In this embodiment, the disc-shaped weight 63 has a circular hole in the middle, and the disc-shaped weight 63 is mounted on the circular rod 62. The center of gravity of the disc-shaped weight 63 coincides with the center line of the circular rod 62.

[0053] With this configuration, the center of gravity of the disc-shaped weight 63 coincides with the center line of the round rod 62, ensuring that the weight's gravity acts vertically downwards on the platform body 61. This avoids horizontal components or additional torques caused by center of gravity shift, ensuring the purity and stability of the applied load and further improving the accuracy of load measurement. Other components and connections are the same as in specific embodiments one, two, three, four, or five.

[0054] Specific implementation method seven: Combination Figures 1 to 6 To illustrate this embodiment, the loading sliding platform 6 of this embodiment also includes a contact wheel 64, which is rotatably mounted on the end of the probe and rolls in cooperation with the upper surface of the lever 7.

[0055] With this configuration, the contact wheel 64 rolls against the upper surface of the lever 7, converting the sliding friction between the probe and the lever 7 into rolling friction. This significantly reduces the impact of contact friction on load transmission, preventing load loss or lever 7 force deviation caused by friction, and ensuring the efficiency and accuracy of load transmission. Other components and connections are the same as in specific implementation methods one, two, three, four, five, or six.

[0056] Specific implementation method eight: Combination Figures 1 to 6 To illustrate this embodiment, the loading sliding platform 6 of this embodiment also includes eight pulley modules, which are arranged perpendicularly to each other at the four corners of the platform body 61.

[0057] The platform body 61 is horizontally set within the rectangular area enclosed by the four L-shaped steels 52 of the loading guide rail 5, and is limited in the horizontal direction by the rolling cooperation of eight pulley modules with the four L-shaped steels 52.

[0058] With this configuration, the eight pulley modules are arranged perpendicularly to each other at the four corners of the platform body 61, limiting the platform body 61 from four directions (front, back, left, and right). This constrains its horizontal displacement and restricts its vertical axis rotation, allowing the platform body 61 to slide only in the vertical direction. Simultaneously, the pulleys and L-shaped steel 52 roll in cooperation, reducing sliding resistance and ensuring the smooth movement of the loaded sliding platform 6, thus guaranteeing the stability of the applied load. Other components and connections are the same as in specific embodiments one, two, three, four, five, six, or seven.

[0059] Specific Implementation Method Nine: Combining Figures 1 to 6 This embodiment describes a pulley module that includes a pulley retainer 65 and two pulleys 66.

[0060] The pulley fixing device 65 is an isosceles trapezoidal plate structure, which is arranged perpendicularly to the platform body 61 and is fixedly connected to the platform body 61 through a slot on the side facing the platform body 61.

[0061] The pulley retainer 65 has a vertically arranged wheel groove on the side facing the L-shaped steel 52. Two pulleys 66 are rotatably installed in the wheel groove at intervals and roll in cooperation with the inner side of the corresponding L-shaped steel 52.

[0062] With this configuration, the pulley retainer 65 is fixedly connected to the platform body 61 via a slot, ensuring a stable assembly and easy disassembly. The two pulleys 66, arranged vertically, roll in contact with the inner side of the L-shaped steel 52, limiting the platform body 61 from both above and below, further enhancing the stability of the platform body 61's sliding motion and preventing tilting during sliding, ensuring that the load transmission direction remains vertical. Other components and connections are the same as in specific embodiments one, two, three, four, five, six, seven, or eight.

[0063] Specific Implementation Method Ten: Combining Figures 1 to 6 In this embodiment, the displacement measurement module 8 uses a non-contact displacement sensor, and the detection end of the non-contact displacement sensor is located directly below the bearing mounting position of the extrusion oil film damper 9.

[0064] With this configuration, the measurement point of the non-contact displacement sensor is directly aligned with the bearing mounting position of the extrusion oil film damper 9, allowing direct detection of displacement changes at this core location and avoiding errors caused by indirect measurement. Simultaneously, the non-contact measurement method does not interfere with the deformation of the extrusion oil film damper 9, ensuring the authenticity and accuracy of the displacement detection data and providing a reliable basis for stiffness calculation. Other components and connections are the same as in specific implementation methods one, two, three, four, five, six, seven, eight, or nine.

[0065] Working principle

[0066] Combination Figures 1 to 6Explanation of the working principle of the gas turbine squeeze film damper stiffness measuring device of the present invention:

[0067] This invention achieves accurate measurement of the stiffness of a squeeze film damper based on the lever torque balance principle and the direct load-displacement measurement method. The specific working process is as follows:

[0068] Test preparation: The test rigid platform 1 is leveled and fixed to ensure sufficient rigidity to avoid deformation during the test; the extrusion oil film damper 9 is fixed by the support fixture 3, which simulates the assembly state of the gas turbine casing to ensure that the installation posture of the extrusion oil film damper 9 is consistent with the actual working state; the loading fixture 4 is embedded inside the extrusion oil film damper 9, and its outer edge of the circular plate is interference-fitted with the damper to simulate the assembly relationship between the rotor bearing and the damper. The middle part of the lever 7 passes through the rectangular hole of the loading fixture 4 and is hinged; the loading sliding platform 6 is installed in the area enclosed by the four L-shaped steels 52 of the loading guide rail 5 through the pulley modules at the four corners. The contact wheel 64 below the circular rod 62 contacts the upper surface of the left end of the lever 7. The displacement measurement module 8 is fixed in the middle of the support fixture 3, and its measurement point is aligned directly below the bearing installation position of the extrusion oil film damper 9.

[0069] Load application: A disc-shaped weight 63 is placed on the round rod 62 of the loading sliding platform 6. The center of gravity of the weight coincides with the center line of the round rod 62. Its gravity acts vertically downward on the platform body 61 and is transmitted to the left end of the lever 7 (the fulcrum of the weight loading) through the contact wheel 64 below the round rod 62, forming a right-hand torque. The right end of the lever 7 is hinged and fixed by the hinge bracket 2 (the fixed hinge fulcrum of the lever). According to the lever torque balance principle, the hinge point between the middle of the lever 7 and the loading fixture 4 (the force fulcrum of the extrusion oil film damper B) will generate a left-hand torque that balances the right-hand torque. The extrusion oil film damper 9 is subjected to a downward force transmitted by the loading fixture 4. The ratio of this force to the weight of the weight is equal to the ratio of the weight force arm L1 to the force arm L2 of the extrusion oil film damper, that is, the ratio of the force on the extrusion oil film damper to the weight of the weight L1 / L2, thus achieving a proportional amplification of the load.

[0070] Displacement detection: The squeeze oil film damper 9 undergoes elastic deformation under the applied force, and its bearing installation position is displaced downward. The displacement measurement module 8 (non-contact displacement sensor) detects and outputs the displacement data at this position in real time. The loading guide rail 5 cooperates with the pulley module of the loading sliding platform 6 to constrain the horizontal displacement and rotation of the platform body 61, ensuring that the weight arm L1 of the lever 7 and the force arm L2 of the squeeze oil film damper remain unchanged during the addition and subtraction of weights, and the load amplification factor is stable.

[0071] Stiffness calculation: Different loads are applied by increasing or decreasing the number of disc-shaped weights 63. The load value and displacement value detected by the displacement measurement module 8 are recorded for each loading. The load-displacement curve of the extrusion oil film damper 9 is plotted. The static bending stiffness of the extrusion oil film damper 9 at the bearing mounting position can be obtained by fitting the curve (stiffness = load / displacement). Through multiple loading tests, the elastic range and stiffness consistency of the extrusion oil film damper 9 can be further verified.

[0072] The above embodiments are only used to illustrate the technical solutions of the present invention, and are not intended to limit it. Although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A device for measuring the stiffness of a gas turbine squeeze film damper, characterized in that, The device includes a test rigid platform (1), a hinged bracket (2), a support fixture (3), a loading fixture (4), a loading guide rail (5), a loading sliding platform (6), a lever (7), a displacement measurement module (8), and a squeeze oil film damper (9). The test rigid platform (1) is arranged horizontally. A vertically arranged support fixture (3) is provided at the top center of the test rigid platform (1). A squeeze oil film damper (9) is installed on the upper part of the support fixture (3) along the length direction of the test rigid platform (1). A loading fixture (4) is embedded inside the squeeze oil film damper (9). The joint between the loading fixture (4) and the squeeze oil film damper (9) is the bearing installation position. The loading fixture (4) is hinged to the lever (7). The left and right sides of the squeeze oil film damper (9) are respectively provided with loading guide rail (5) and hinge bracket (2) vertically fixed to the top of the test rigid platform (1). One end of the lever (7) is hinged to the hinge bracket (2), and the other end of the lever (7) is located directly below the loading sliding platform (6). The loading sliding platform (6) can slide freely up and down along the loading guide rail (5), and a vertically arranged probe is provided in the middle of the lower part of the loading sliding platform (6). The probe contacts the upper end surface of the lever (7). A displacement measurement module (8) is provided directly below the extrusion oil film damper (9). The displacement measurement module (8) is installed in the middle of the support fixture (3), and the detection end of the displacement measurement module (8) is set in accordance with the bearing installation position.

2. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 1, characterized in that, The loading fixture (4) is a circular plate with the same thickness as the rotor bearing. A rectangular hole is opened in the middle of the circular plate. The lever (7) is a rod-shaped structure with a rectangular cross-section. The middle part of the lever (7) passes through the rectangular hole of the circular plate and is hinged to the loading fixture (4). The outer edge of the circular plate is fixedly connected to the extrusion oil film damper (9) through an interference fit between the hole and the shaft.

3. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 2, characterized in that, The loading guide rail (5) includes a guide rail fixing base plate (51) and four L-shaped steel bars (52). The guide rail fixing base plate (51) is arranged horizontally and fixedly connected to the top of the test rigid platform (1). The top of the guide rail fixing base plate (51) is fixedly connected to four L-shaped steels (52) perpendicular to the ground. The four L-shaped steels (52) are evenly arranged around the circumference.

4. The gas turbine squeeze film damper stiffness measuring device according to claim 3, characterized in that, Four L-shaped steel bars (52) are arranged in pairs on the front and back sides of the lever (7) axis, and the free end of the lever (7) passes between the two L-shaped steel bars (52).

5. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 4, characterized in that, The loading sliding platform (6) includes a platform body (61), a round rod (62), and multiple disc-shaped weights (63). The platform body (61) is a square plate with a certain thickness. The round rod (62) passes vertically through the upper and lower end faces of the center of the platform body (61) and is fixedly connected by an interference fit through the shaft hole. The portion of the round rod (62) located above the platform body (61) is used to limit the horizontal displacement of the disc-shaped weight (63), while the portion located below the platform body (61) forms a probe that contacts the lever (7).

6. The gas turbine squeeze film damper stiffness measuring device according to claim 5, characterized in that, A circular hole is opened in the middle of the disc-shaped weight (63). The disc-shaped weight (63) is installed on the round rod (62). The center of gravity of the disc-shaped weight (63) coincides with the center line of the round rod (62).

7. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 6, characterized in that, The loading sliding platform (6) also includes a contact wheel (64), which is rotatably mounted on the end of the probe and rolls into contact with the upper surface of the lever (7).

8. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 7, characterized in that, The loading sliding platform (6) also includes eight pulley modules, which are arranged perpendicularly to each other at the four corners of the platform body (61); The platform body (61) is horizontally set within the rectangular area enclosed by the four L-shaped steels (52) of the loading guide rail (5), and the horizontal limit is achieved by the rolling cooperation of eight pulley modules with the four L-shaped steels (52).

9. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 8, characterized in that, Each pulley module includes a pulley retainer (65) and two pulleys (66). The pulley fastener (65) is an isosceles trapezoidal plate structure, which is arranged perpendicularly to the platform body (61) and is fixedly connected to the platform body (61) through a slot on the side facing the platform body (61); The pulley retainer (65) has vertically arranged wheel grooves on the side facing the L-shaped steel (52). Two pulleys (66) are rotatably installed in the wheel grooves at intervals and roll into contact with the inner side of the corresponding L-shaped steel (52).

10. The device for measuring the stiffness of a gas turbine squeeze film damper according to claim 1, characterized in that, The displacement measurement module (8) uses a non-contact displacement sensor, and the detection end of the non-contact displacement sensor is located directly below the bearing mounting position of the extrusion oil film damper (9).

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