Test method of radial gap between moving and static parts of steam turbine, storage medium and electronic device

Abstract

The application provides a steam turbine radial dynamic-static gap testing method, a storage medium and an electronic device. The steam turbine radial dynamic-static gap testing method comprises the following steps: obtaining rotor parameters, cylinder offset and bearing oil film thickness of a steam turbine; determining a deflection value of the steam turbine according to the rotor parameters; the deflection value comprises a static deflection value and a dynamic deflection value; correcting the bearing oil film thickness, combining the deflection value and the corrected bearing oil film thickness to construct a dynamic running position vector of the rotor; correcting a dynamic running position of a cylinder by using the cylinder offset; and determining the radial dynamic-static gap at each axial position of the steam turbine according to the dynamic running position vector of the rotor and the dynamic running position of the cylinder. The application realizes real-time analysis of the radial gap change at each axial position of the steam turbine by means of an online simulation testing method on the original vibration testing system.

Description

Technical Field

[0001] This invention belongs to the technical field of power machinery, and relates to a method for testing dynamic and static clearance, particularly a method for testing radial dynamic and static clearance of a steam turbine, a storage medium, and electronic equipment. Background Technology

[0002] Vibration failures in rotating machinery are among the most critical performance indicators during power plant operation, and are closely related to the plant's profitability. Dynamic-static rubbing is one of the most common and frequent vibration failures in the field. Once it occurs, the location of the dynamic-static rubbing is difficult to pinpoint, making it extremely challenging to eliminate and posing significant difficulties for power plant operation.

[0003] Currently, the only method that can be used to measure the vibration at the two support bearings of the rotor is through vibration. However, due to the very limited number of vibration measurement points on site, it is impossible to determine the dynamic and static clearance inside the cylinder from the vibration signals of the two bearings.

[0004] Therefore, how to provide a test method, storage medium, and electronic equipment for the radial dynamic and static clearance of a steam turbine to solve the shortcomings of existing technologies, such as the inability to analyze the radial dynamic and static clearance at various axial positions of a steam turbine in real time, has become a technical problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0005] In view of the shortcomings of the prior art described above, the purpose of this invention is to provide a test method, storage medium and electronic device for the radial dynamic and static clearance of a steam turbine, so as to solve the problem that the prior art cannot analyze the radial dynamic and static clearance at various axial positions of a steam turbine in real time.

[0006] To achieve the above and other related objectives, the present invention provides a method for testing the radial dynamic and static clearance of a steam turbine. The method includes: acquiring the rotor parameters, cylinder offset, and bearing oil film thickness of the steam turbine; determining the deflection value of the steam turbine based on the rotor parameters; the deflection value includes a static deflection value and a dynamic deflection value; correcting the bearing oil film thickness; constructing a dynamic operating position vector of the rotor by combining the deflection value and the corrected bearing oil film thickness; correcting the dynamic operating position of the cylinder using the cylinder offset; and determining the radial dynamic and static clearance at each axial position of the steam turbine based on the dynamic operating position vector of the rotor and the dynamic operating position of the cylinder.

[0007] In one embodiment of the present invention, the step of determining the deflection value of the steam turbine based on the rotor parameters includes: determining the static deflection value based on the length, mass, diameter, and moment of inertia of the rotor; and determining the dynamic deflection value based on the length, mass, diameter, moment of inertia, rotational speed, and temperature of the rotor.

[0008] In one embodiment of the present invention, the step of correcting the bearing oil film thickness includes: determining the relationship between the bearing oil film thickness and the rotor speed based on the structural relationship between the rotor and the bearing; and using the relationship between the bearing oil film thickness and the rotor speed to interpolate the obtained bearing oil film thickness to determine the unobtained bearing oil film thickness.

[0009] In one embodiment of the present invention, the cylinder offset includes the cylinder installation pre-lift amount and the cylinder thermal expansion amount; the step of using the cylinder offset to correct the dynamic operating position of the cylinder includes: using the cylinder installation pre-lift amount and the cylinder thermal expansion amount to pre-correct the dynamic operating position of the cylinder.

[0010] In one embodiment of the present invention, the step of obtaining the cylinder offset includes: obtaining the cylinder offset by means of a finite element method and a preset empirical value.

[0011] In one embodiment of the present invention, the dynamic running position vector is a feature vector; the step of constructing the rotor's dynamic running position vector by combining the deflection value and the corrected bearing oil film thickness includes: determining the rotor's displacement and the angle of the displacement by combining the deflection value and the corrected bearing oil film thickness; and determining the rotor's displacement and the angle of the displacement as feature vectors.

[0012] In one embodiment of the present invention, the step of determining the radial dynamic and static clearances at each axial position of the turbine based on the dynamic operating position vector of the rotor and the dynamic operating position of the cylinder includes: determining the clearance change between the rotor and the cylinder based on the dynamic operating position of the cylinder; and performing algebraic calculations on the clearance change and the dynamic operating position vector to determine the radial dynamic and static clearances at each axial position of the turbine.

[0013] To achieve the above and other related objectives, another aspect of the present invention provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the method for testing the radial dynamic and static clearance of a steam turbine.

[0014] To achieve the above and other related objectives, a final aspect of the present invention provides an electronic device, comprising: a processor and a memory; the memory for storing a computer program, and the processor for executing the computer program stored in the memory to cause the electronic device to perform the aforementioned method for testing the radial dynamic and static clearance of a steam turbine.

[0015] As described above, the test method, storage medium, and electronic equipment for the radial dynamic and static clearance of a steam turbine according to the present invention have the following beneficial effects:

[0016] This invention utilizes the location and fixing method of the bearing vibration sensor already installed on site, as well as the sensor signal type, to propose a measurement method for online simulation of radial dynamic and static clearance. Specifically, it corrects the dynamic deflection of the turbine rotor, the bearing oil film data, and the static data of the cylinder installation. Using the eigenvalue vector method, it describes the dynamic operating position of the turbine rotor and cylinder, and realizes real-time analysis of the radial dynamic and static clearance at various axial positions of the turbine. Attached Figure Description

[0017] Figure 1 The diagram shown is a schematic flowchart of a test method for the radial dynamic and static clearance of a steam turbine according to an embodiment of the present invention.

[0018] Figure 2 The diagram shown is a rotor deflection model diagram in one embodiment of the test method for radial dynamic and static clearance of a steam turbine according to the present invention.

[0019] Figure 3 The diagram shows a shaft segment under stress in one embodiment of the test method for radial dynamic and static clearance of a steam turbine according to the present invention.

[0020] Figure 4 The diagram shows the bearing and rotor positions in one embodiment of the test method for radial dynamic and static clearance of a steam turbine according to the present invention.

[0021] Figure 5 The diagram shown is a schematic diagram of bearing dynamic characteristic analysis in one embodiment of the test method for radial dynamic and static clearance of steam turbines according to the present invention.

[0022] Figure 6 The diagram shown is a simplified bearing model in one embodiment of the test method for radial dynamic and static clearance of a steam turbine according to the present invention.

[0023] Figure 7 The diagram shows a dynamic and static clearance in one embodiment of the test method for the radial dynamic and static clearance of a steam turbine according to the present invention.

[0024] Figure 8 The diagram shown is a structural connection diagram of the electronic device of the present invention in one embodiment.

[0025] Component designation explanation

[0026] 8 Electronic devices

[0027] 81 processor

[0028] 82 Memory

[0029] Steps S11 to S15 Detailed Implementation

[0030] The following specific examples illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific embodiments, and various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention. It should be noted that, unless otherwise specified, the following embodiments and features described therein can be combined with each other.

[0031] It should be noted that the illustrations provided in the following embodiments are only schematic representations of the basic concept of the present invention. Therefore, the illustrations only show the components related to the present invention and are not drawn according to the actual number, shape and size of the components in the actual implementation. In the actual implementation, the form, quantity and proportion of each component can be arbitrarily changed, and the layout of the components may also be more complex.

[0032] The test method, storage medium, and electronic equipment for the radial dynamic and static clearance of a steam turbine described in this invention can be implemented on the existing vibration measurement system. Through online simulation testing, the changes in radial clearance at various axial positions of the steam turbine can be analyzed in real time.

[0033] The following will combine Figures 1 to 8 This paper elaborates on the principle and implementation of a test method, storage medium and electronic equipment for the radial dynamic and static clearance of a steam turbine according to an embodiment, so that those skilled in the art can understand the test method, storage medium and electronic equipment for the radial dynamic and static clearance of a steam turbine according to this embodiment without creative labor.

[0034] Please see Figure 1 The diagram shows a schematic flowchart of one embodiment of the test method for radial dynamic and static clearance of a steam turbine according to the present invention. Figure 1 As shown, the test method for the radial dynamic and static clearance of the steam turbine specifically includes the following steps:

[0035] S11, obtain the turbine rotor parameters, cylinder offset and bearing oil film thickness.

[0036] In one embodiment, the rotor parameters include the rotor's length, mass, diameter, moment of inertia, rotational speed, and temperature.

[0037] In one embodiment, the cylinder offset is obtained by finite element method and preset empirical values.

[0038] S12, determine the deflection value of the steam turbine based on the rotor parameters; the deflection value includes static deflection value and dynamic deflection value.

[0039] In one embodiment, the static deflection value is determined based on the length, mass, diameter, and moment of inertia of the rotor.

[0040] The dynamic deflection value is determined based on the rotor's length, mass, diameter, moment of inertia, rotational speed, and temperature.

[0041] Please see Figure 2 The diagram shows a rotor deflection model in one embodiment of the turbine radial dynamic and static clearance testing method of the present invention. Figure 2 As shown, specifically, the calculation method for rotor static deflection is the transfer matrix method or other existing methods for calculating static deflection.

[0042] In the rotor deflection model, the bending deformation formula of the beam axis, which can be expressed by curvature in the case of pure bending and within the linear elastic range, is as follows:

[0043]

[0044] Where ρ represents the radius of curvature, M represents the bending moment, E represents the elastic modulus, and I is the moment of inertia. Thus, curvature expresses the relationship between the beam's deflection curve and the load. In the case of bending, the beam's cross-section experiences both bending moment and shear force, the latter causing additional bending deformation. For common slender beams, this additional bending deformation is negligible, therefore the above formula still applies to bending. In this case, both the bending moment and the radius of curvature are functions of x, i.e.:

[0045]

[0046] From differential calculus, we know that the curvature at any point on a plane is:

[0047]

[0048] Substituting Formula 3 into Formula 2, since in a flat deflection curve, the angle... It is a very small quantity, therefore Compared to 1, it can be ignored, therefore it can be simplified to:

[0049]

[0050] Formula 4 is the approximate differential equation for the deflection curve of the beam.

[0051] For a constant diameter, EI is constant, and under small deformation conditions... Therefore, formula 4 can be transformed into:

[0052]

[0053]

[0054] In Equations 5 and 6, C1 and C2 can be determined by the known displacement conditions on the beam.

[0055] Please see Figure 3 The diagram shows a stress diagram of a shaft segment in one embodiment of the test method for radial dynamic and static clearance of a steam turbine according to the present invention. Figure 3 As shown, we take the Jth segment of the shaft for study, where the bending moment is represented by N.

[0056] Depend on Figure 3 The following relationship can be obtained:

[0057] Q j+1 =Q j (Formula 7)

[0058] N j+1 =N j +Q j l j (Formula 8)

[0059]

[0060]

[0061] Combining formulas 7 to 10, we obtain the following matrix expression:

[0062]

[0063] Formula 11 is the transfer matrix, which is transferred from segment j of the rotor to segment j+1, and calculated segment by segment to obtain the static deflection of each shaft segment.

[0064] Furthermore, the dynamic deflection value is mainly affected by temperature. That is, compared with the static deflection, only the elastic modulus E is different. The calculation method is the same as the calculation principle of the static deflection.

[0065] The parameters for static deflection calculation only include: discretized rotor parameters (specifically, the rotor is discretized into many segments, represented by length, mass, diameter, and moment of inertia). The static deflection value is obtained through dynamic calculations. Static deflection mainly refers to the deflection caused by the rotor's own weight, without the influence of high temperatures. The main difference between static and dynamic deflection lies in the boundary parameters; dynamic deflection is primarily based on changes in the rotor's rotational speed and temperature, which cause changes in the elastic modulus.

[0066] Specifically, for the calculation of dynamic deflection values, rotor dynamics mainly involves solving the mechanical equations of vibration. The vibration dynamics equations describe the relationship between vibration (displacement) values, system stiffness, system damping, and excitation force in the physical model.

[0067] In practical applications, the differential equation of motion for the rotor system is as follows:

[0068]

[0069] Where M is the mass matrix; C is the damping matrix, an asymmetric matrix; G is the gyroscope matrix, an antisymmetric matrix; K is the symmetric part of the stiffness matrix; S is the asymmetric part of the stiffness matrix; and F is the excitation force matrix. Each matrix is ​​often a function of the rotational speed.

[0070] According to the equation of Formula 12, the vertical dynamic deflection and angle, and the horizontal dynamic deflection and angle of each node and shaft segment of the rotor can be obtained by using the preset rotor dynamic analysis program, as shown in Table 1, which contains the dynamic deflection and phase values ​​of the rotor at different speeds.

[0071] Table 1. Rotor dynamic deflection and phase values ​​at different speeds.

[0072]

[0073] S13, correct the bearing oil film thickness, and construct the dynamic running position vector of the rotor by combining the deflection value and the corrected bearing oil film thickness.

[0074] In one embodiment, the relationship between the bearing oil film thickness and the rotor speed is determined based on the structural relationship between the rotor and the bearing; the obtained bearing oil film thickness is interpolated using the relationship between the bearing oil film thickness and the rotor speed to determine the unobtained bearing oil film thickness.

[0075] Specifically, the correction value for the bearing oil film is obtained by analyzing the dynamic response under different speed and operating conditions using the different oil film characteristics during the acceleration process. Since sliding bearings generate an oil film during operation, the thickness of this oil film affects the overall calculation results. Therefore, dynamic calculations and analyses need to be performed on each radial bearing to obtain the correction value for the oil film thickness.

[0076] Please see Figure 4 The diagram shows the bearing and rotor positions in one embodiment of the turbine radial dynamic and static clearance testing method of the present invention. Figure 4 As shown, after the rotor rotates, an oil film forms between the bearing and the rotor. Once the structure of the rotor and bearing is determined, the oil film thickness is related to the rotor speed. Dynamic calculations can obtain the oil film thickness at different speeds. To improve calculation efficiency, an Excel spreadsheet can be used for linear interpolation to obtain oil film thickness values ​​that are not listed or calculated.

[0077] Please see Figure 5The diagram shows a schematic analysis of the bearing dynamic characteristics in one embodiment of the test method for the radial dynamic and static clearance of a steam turbine according to the present invention. When the rotor rotates at an angular frequency ω, lubricating oil is drawn into the converging oil wedge between the two surfaces, generating oil film pressure. In steady state, the weight of the rotor is balanced by the resultant force of the oil film pressure, at which point the journal center automatically stabilizes at a certain static operating point position, usually represented by the eccentricity e of the journal center off from the bearing center O.

[0078] As the rotational speed ω gradually increases from 0, the entrainment effect also gradually strengthens, and the oil film force further lifts the rotor. Under dynamic conditions, in addition to the aforementioned static oil film pressure, the displacement and velocity disturbances caused by journal vibration will also generate a dynamic oil film force. Under the combined action of external excitation and dynamic oil film force, the rotor will maintain a small vibration near its static equilibrium position. When the disturbance is minute, the relationship between the force change and the disturbance simplifies to a linear relationship. The following section combines... Figure 5 The calculation and analysis process of the dynamic characteristic coefficient of oil film.

[0079] The two components of the bearing capacity F are:

[0080]

[0081] Where P is the oil film pressure (gauge pressure), r is the journal radius, z is the axial coordinate, and φa and φb are the angles at the beginning and end of the bearing, respectively.

[0082] Bearing capacity W represents the radial load acting on the bearing.

[0083] The load-carrying capacity of a bearing is often expressed as a dimensionless load-carrying capacity coefficient φ. P This indicates that the relative unit is taken as Then we have:

[0084]

[0085] in, η is the dynamic viscosity of the lubricating oil, and U is the journal circumferential speed.

[0086] Then, the following definition is made:

[0087] kij (i, j = x, y): oil film stiffness coefficient, kij is the force generated by a unit displacement disturbance in the j direction in the i direction;

[0088] cij (i, j = x, y): oil film damping coefficient, cij is the force generated by a unit velocity disturbance in the j direction in the i direction.

[0089] The dynamic characteristics of the oil film are typically characterized using eight stiffness and damping coefficients. By definition, by differentiating the disturbance quantities contained in the resultant force of the dynamic oil film with respect to Fx and Fy, we can obtain kij and cij as follows:

[0090]

[0091]

[0092] If take When y = Cy, the corresponding dimensionless coefficients (oil film stiffness coefficient and damping coefficient) are as follows:

[0093]

[0094] Please see Figure 6 The diagram shows a simplified bearing model in one embodiment of the turbine radial dynamic and static clearance testing method of the present invention. Figure 6 As shown, when performing dynamic analysis on a system, the effect of bearing oil film force can usually be simplified to a spring-damping model.

[0095] The dynamic characteristics of the oil film are represented by the oil film stiffness coefficient kij and the oil film damping coefficient cij in four directions xx, xy, yx, and yy. The stiffness coefficient represents the increase in force caused by a unit displacement disturbance of the journal, and the damping coefficient characterizes the increase in force caused by a unit velocity disturbance of the journal.

[0096] The minimum thickness in the radial direction of each radial support bearing can be calculated using the above formula, allowing the dynamic position of the rotor to be corrected through program execution. For example, the calculated oil film information can be listed and managed to form the radial thickness correction values ​​for each bearing in Table 2.

[0097] Table 2 Radial thickness correction values ​​for each bearing

[0098]

[0099] The radial position of the rotor relative to the stator under hot conditions can be obtained using the correction values ​​in Table 2. The multi-boundary correction mode allows the calculated simulation results to better reflect the actual situation, thus improving the accuracy of the simulation.

[0100] In one embodiment, the dynamic operating position vector is a feature vector. The displacement and angle of the rotor are determined by combining the deflection value and the corrected bearing oil film thickness; the displacement and angle of the rotor are then defined as the feature vector.

[0101] Specifically, to match the rapidly changing vibration signals, eigenvalue vectors are used to describe the dynamic operating positions of the turbine rotor and cylinders, thus meeting the signal requirements. Since real-time iterative calculations cannot meet the needs of actual field operation, it is necessary to extract eigenvectors and use vector interpolation to reduce the computational load, improve computational efficiency, and ensure real-time data feedback during the acceleration process.

[0102] S14, using the cylinder offset, correct the dynamic operating position of the cylinder.

[0103] In one embodiment, the cylinder offset includes the cylinder installation pre-lift and the cylinder thermal expansion. The cylinder's dynamic operating position is pre-corrected using the cylinder installation pre-lift and the cylinder thermal expansion.

[0104] Specifically, stationary components such as turbine cylinders will have offsets during installation. The dynamic operating position of the cylinder is described by making corrections during the precise calculation process, providing a linear correction method to describe the position of the cylinder.

[0105] S15, based on the dynamic operating position vector of the rotor and the dynamic operating position of the cylinder, determine the radial dynamic and static clearances at each axial position of the turbine. Therefore, the dynamic and static clearances can be analyzed and detected online in real time using computer equipment.

[0106] In one embodiment, the clearance change between the rotor and the cylinder is determined based on the dynamic operating position of the cylinder; the clearance change and the dynamic operating position vector are algebraically calculated to determine the radial dynamic and static clearances at each axial position of the turbine.

[0107] Please see Figure 7 The diagram shows a schematic representation of the dynamic and static clearance in one embodiment of the turbine radial dynamic and static clearance testing method of the present invention. Figure 7 As shown, the characteristic vector refers to the rotor displacement and the angle of displacement obtained through dynamic calculations during the dynamic process (under operating speed and under heating conditions). The dynamic static clearance can be obtained by algebraically calculating the design clearance between the rotor and cylinder using the characteristic vector.

[0108] It should be noted that the calculation processes for each correction are independent of each other and have no sequential relationship; that is, the calculations are not sequential. This invention, through the correction calculations of various data, can calculate and obtain the radial dynamic and static clearances at each axial position of the steam turbine in real time. The linear correction method described in this invention can be an interpolation calculation method or other methods that can achieve the correction purpose.

[0109] Therefore, the online simulation test of radial dynamic and static clearance mainly uses simulation methods, utilizing eigenvalue vectors to describe the dynamic positions of the rotor and cylinder. Simultaneously, it incorporates bearing oil film factors and cylinder installation factors to correct the dynamic data. The corresponding data is then set into the appropriate program, enabling real-time monitoring of the radial dynamic and static clearance. Vibration signals are rapidly changing signals. To meet the response requirements of rapidly changing vibration signals in the field, the dynamic positions of the turbine rotor and cylinder must match the characteristics of the rapidly changing signal. A method for calculating the eigenvalues ​​of dynamic analysis data is used to meet the needs of online real-time simulation testing.

[0110] The scope of protection of the test method for radial dynamic and static clearance of steam turbines described in this invention is not limited to the order of steps listed in this embodiment. Any solution achieved by adding, subtracting, or replacing steps in the prior art based on the principles of this invention is included within the scope of protection of this invention.

[0111] This embodiment provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements a method for testing the radial dynamic and static clearance of a steam turbine.

[0112] Those skilled in the art will understand that all or part of the steps of the above-described method embodiments can be implemented using computer program-related hardware. The aforementioned computer program can be stored in a computer-readable storage medium. When executed, the program performs the steps of the above-described method embodiments; and the aforementioned computer-readable storage medium includes various computer storage media capable of storing program code, such as ROM, RAM, magnetic disks, or optical disks.

[0113] Please see Figure 8 The diagram shows a structural connection schematic of the electronic device of the present invention in one embodiment. Figure 8 As shown, this embodiment provides an electronic device 8, specifically including: a processor 81 and a memory 82; the memory 82 is used to store a computer program, and the processor 81 is used to execute the computer program stored in the memory 82, so that the electronic device 8 performs each step of the test method for the radial dynamic and static clearance of the steam turbine.

[0114] The processor 81 mentioned above can be a general-purpose processor, including a central processing unit (CPU), a network processor (NP), etc.; it can also be a digital signal processor (DSP), an application-specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, or discrete hardware components.

[0115] The aforementioned memory 82 may include random access memory (RAM) or non-volatile memory, such as at least one disk storage device.

[0116] In summary, the test method, storage medium, and electronic equipment for the radial dynamic and static clearance of a steam turbine described in this invention can utilize the location and fixing method of the bearing vibration sensors already installed on-site, as well as the sensor signal type, to propose an online simulation measurement method for radial dynamic and static clearance. Specifically, it corrects the dynamic deflection of the steam turbine rotor, the bearing oil film data, and the static data of the cylinder installation. Using the eigenvalue vector method, it describes the dynamic operating position of the steam turbine rotor and cylinder, realizing real-time analysis of the radial dynamic and static clearance at various axial positions of the steam turbine. This invention effectively overcomes the various shortcomings of the prior art and has high industrial application value.

[0117] The above embodiments are merely illustrative of the principles and effects of the present invention and are not intended to limit the invention. Any person skilled in the art can modify or alter the above embodiments without departing from the spirit and scope of the present invention. Therefore, all equivalent modifications or alterations made by those skilled in the art without departing from the spirit and technical concept disclosed in the present invention should still be covered by the claims of the present invention.

Claims

1. A method for testing the radial dynamic and static clearance of a steam turbine, characterized in that, The test method for the radial dynamic and static clearance of the steam turbine includes: Obtain the turbine rotor parameters, cylinder offset, and bearing oil film thickness; The deflection value of the steam turbine is determined based on the rotor parameters; the deflection value includes static deflection value and dynamic deflection value; The bearing oil film thickness is corrected, and the dynamic operating position vector of the rotor is constructed by combining the deflection value and the corrected bearing oil film thickness. Correcting the bearing oil film thickness includes: determining the relationship between the bearing oil film thickness and the rotor speed based on the structural relationship between the rotor and the bearing; using the relationship between the bearing oil film thickness and the rotor speed, interpolating the acquired bearing oil film thickness to determine the unacquired bearing oil film thickness; the dynamic operating position vector is a feature vector. Constructing the dynamic operating position vector of the rotor by combining the deflection value and the corrected bearing oil film thickness includes: determining the rotor displacement and the angle of the displacement by combining the deflection value and the corrected bearing oil film thickness; the rotor displacement and the angle of the displacement are determined as feature vectors. The cylinder offset is used to correct the dynamic operating position of the cylinder; the cylinder offset includes the cylinder installation pre-lift and the cylinder thermal expansion, and the cylinder dynamic operating position is pre-corrected using the cylinder installation pre-lift and the cylinder thermal expansion. Based on the dynamic operating position vector of the rotor and the dynamic operating position of the cylinder, the radial dynamic and static clearances at each axial position of the turbine are determined; based on the dynamic operating position of the cylinder, the clearance variation between the rotor and the cylinder is determined; the clearance variation and the dynamic operating position vector are algebraically calculated to determine the radial dynamic and static clearances at each axial position of the turbine.

2. The test method for radial dynamic and static clearance of a steam turbine according to claim 1, characterized in that, The step of determining the deflection value of the steam turbine based on the rotor parameters includes: The static deflection value is determined based on the rotor's length, mass, diameter, and moment of inertia. The dynamic deflection value is determined based on the rotor's length, mass, diameter, moment of inertia, rotational speed, and temperature.

3. The method for testing the radial dynamic and static clearance of a steam turbine according to claim 1, characterized in that, The step of obtaining the cylinder offset includes: The cylinder offset is obtained by finite element method and preset empirical values.

4. A computer-readable storage medium having a computer program stored thereon, characterized in that, When executed by a processor, the computer program implements the test method for the radial dynamic and static clearance of a steam turbine as described in any one of claims 1 to 3.

5. An electronic device, characterized in that, include: Processor and memory; The memory is used to store a computer program, and the processor is used to execute the computer program stored in the memory to cause the electronic device to perform the test method for the radial dynamic and static clearance of the steam turbine as described in any one of claims 1 to 3.

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