Dynamic balance method for critical rotating speed vibration of single-cylinder steam turbine rotor and related device

Abstract

The invention discloses a dynamic balance method and related device for critical rotating speed vibration of a single-cylinder steam turbine rotor, and the method comprises the following steps: judging whether weighting needs to be carried out on a steam-engine coupling or not, and when weighting needs to be carried out on the steam-engine coupling, weighting is carried out on the steam-engine coupling; determining a dynamic balance influence coefficient according to the vibration vector and the weighting vector of the steam turbine rotor before and after weighting; and according to the dynamic balance influence coefficient, establishing a relationship among the vibration vector under the critical rotation speed of the single-cylinder steam turbine rotor, the dynamic balance influence coefficient and an emphasis vector, adopting an ideal point method to obtain a final emphasis vector, and carrying out dynamic balance of the critical rotation speed vibration of the single-cylinder steam turbine rotor according to the final emphasis vector. According to the method and the related device, on-site high-speed dynamic balance can be carried out on the rotor of the single-cylinder steam turbine on the premise that cylinder uncovering is not carried out.

Description

Technical Field

[0001] The invention belongs to the field of power machinery engineering and relates to a dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor and a related device. Background Art

[0002] Balancing involves adjusting the rotor's mass distribution to reduce vibrations and bearing dynamic reaction forces caused by imbalance to within acceptable limits. For example, in steam turbine generators, imbalance accounts for approximately 70% of all vibration failures. On-site dynamic balancing is the best way to address these vibration issues.

[0003] Single-cylinder steam turbines are widely used in industrial production. During use, due to various possible reasons, the main shaft of the turbine rotor may bend, resulting in uneven mass distribution relative to the axis when the rotor rotates, generating centrifugal force, thereby causing dynamic balance failure and causing the turbine rotor to vibrate excessively when passing the critical speed, seriously affecting the normal start and shutdown of the unit.

[0004] There are two ways to repair rotor dynamic balance. One is to remove the rotor and return it to the factory for repair, which is labor-intensive and time-consuming, with high repair costs and a lot of downtime losses. The other is to perform high-speed dynamic balancing repair directly on site, without removing the rotor, which is quick and easy. However, for the vast majority of single-cylinder steam turbines, there is no dedicated on-site dynamic balancing weighting entrance on the cylinder body. Without removing the cylinder, it is impossible to perform on-site dynamic balancing on the rotor. If the cylinder is removed for weighting, it will also consume a lot of time, manpower and financial resources, and it is easy to over- or under-adjust due to misjudgment. Based on this, it is particularly urgent and important to be able to perform on-site high-speed dynamic balancing on the single-cylinder steam turbine rotor without removing the cylinder, so as to improve its problem of excessive critical speed vibration. Summary of the Invention

[0005] The purpose of the present invention is to overcome the shortcomings of the above-mentioned prior art and provide a dynamic balancing method and related device for the critical speed vibration of a single-cylinder steam turbine rotor. This method and related device can perform on-site high-speed dynamic balancing of a single-cylinder steam turbine rotor without removing the cylinder.

[0006] To achieve the above object, the present invention discloses a dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor, comprising the following steps:

[0007] Determine whether it is necessary to add weight to the steam-generator coupling, and if so, add weight to the steam-generator coupling;

[0008] Determine the dynamic balance influence coefficient based on the vibration vector and weighting vector of the steam turbine rotor before and after weighting;

[0009] According to the dynamic balance influence coefficient, the relationship between the vibration vector, dynamic balance influence coefficient and weighting vector at the critical speed of the single-cylinder steam turbine rotor is established, the ideal point method is used to obtain the final weighting vector, and the dynamic balance of the critical speed vibration of the single-cylinder steam turbine rotor is performed according to the final weighting vector.

[0010] The further improvement of the dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to the present invention is as follows:

[0011] Furthermore, the process of determining whether weighting is required on the steam-generator coupling is as follows:

[0012] Determine the rotation direction of a single-cylinder steam turbine generator set;

[0013] Obtain the actual installation position information of the key phase sensor and relative shaft vibration sensor of the rotating equipment under test;

[0014] During the start-up and shutdown of the steam turbine generator set, relative shaft vibration data of the front and rear bearings of the steam turbine rotor at the critical speed are measured by the key phase sensor and the relative shaft vibration sensor; and the relative shaft vibration data of the front and rear bearings of the generator rotor at the critical speed are recorded at the same time;

[0015] Based on the relative shaft vibration data at the front and rear bearings of the steam turbine rotor and the relative shaft vibration data at the front and rear bearings of the generator rotor, determine whether the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°. When the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°, weighting is applied to the steam-generator coupling.

[0016] Furthermore, the dynamic balance influence coefficient is:

[0017]

[0018] in, is a vector operator, called the dynamic balance influence coefficient, is the vibration vector of the turbine rotor before weighting, is the vibration vector of the turbine rotor after weighting, is the trial weight vector.

[0019] Furthermore, the final weight vector is:

[0020]

[0021] Get the ideal weight of each measuring point: M Tc前ideal 、M Tc后ideal 、M Gc前ideal And the corresponding ideal weighting angle: δ Tc前ideal , δ Tc后ideal, δ Gc前ideal .

[0022] Furthermore, the process of obtaining the actual installation position information of the key phase sensor and the relative shaft vibration sensor of the rotating equipment under test is as follows:

[0023] Measure the angle θ formed between the actual installation position of the key phase sensor and the horizontal or vertical midpoint plane;

[0024] Measure the angle between the relative shaft vibration sensor and the key phase sensor actually installed on the left side Measure the angle between the relative shaft vibration sensor and the key phase sensor actually installed on the right side

[0025] The present invention discloses a dynamic balancing system for critical speed vibration of a single-cylinder steam turbine rotor, comprising:

[0026] a first judgment module, configured to judge whether it is necessary to implement weighting on the steam-generator coupling, and if it is necessary to implement weighting on the steam-generator coupling, implement weighting on the steam-generator coupling;

[0027] A first determining module is used to determine a dynamic balance influence coefficient based on the vibration vector and the weighting vector of the steam turbine rotor before and after weighting is implemented;

[0028] The balancing module is used to establish the relationship between the vibration vector, dynamic balance influence coefficient and weighting vector at the critical speed of the single-cylinder steam turbine rotor according to the dynamic balance influence coefficient, adopt the ideal point method to obtain the final weighting vector, and perform dynamic balancing of the critical speed vibration of the single-cylinder steam turbine rotor according to the final weighting vector.

[0029] The further improvement of the dynamic balancing system for critical speed vibration of a single-cylinder steam turbine rotor according to the present invention is as follows:

[0030] Furthermore, the first judgment module includes:

[0031] The second determining module is used to determine the rotation direction of the single-cylinder steam turbine generator set;

[0032] An acquisition module is used to obtain the actual installation position information of the key phase sensor and the relative shaft vibration sensor of the rotating equipment under test;

[0033] The detection module is used to obtain relative shaft vibration data of the front and rear bearings of the steam turbine rotor at the critical speed through the key phase sensor and the relative shaft vibration sensor during the start-up and shutdown process of the steam turbine generator set; and simultaneously record the relative shaft vibration data of the front and rear bearings of the generator rotor at the critical speed;

[0034] The second judgment module is used to judge whether the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90° based on the relative shaft vibration data at the front and rear bearings of the steam turbine rotor and the relative shaft vibration data at the front and rear bearings of the generator rotor. When the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°, weighting is applied to the steam-generator coupling.

[0035] Furthermore, the final weight vector is:

[0036]

[0037] Get the ideal weight of each measuring point: M Tc前ideal 、M Tc后ideal 、M Gc前ideal And the corresponding ideal weighting angle: δ Tc前ideal , δ Tc后ideal , δ Gc前ideal .

[0038] The present invention discloses a computer device, comprising a memory, a processor, and a computer program stored in the memory and executable on the processor. When the processor executes the computer program, the steps of a dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor are implemented.

[0039] The present invention discloses a computer-readable storage medium storing a computer program. When the computer program is executed by a processor, the computer program implements the steps of a dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor.

[0040] The present invention has the following beneficial effects:

[0041] During specific operation, the dynamic balancing method and related device for the critical speed vibration of a single-cylinder steam turbine rotor described in the present invention use the vibration vector and weighting vector of the steam turbine rotor before and after weighting to determine the dynamic balancing influence coefficient based on an external sensor, and then obtain the final weighting vector based on the ideal point method. The dynamic balancing of the critical speed vibration of the single-cylinder steam turbine rotor is performed according to the final weighting vector. The problem of large critical speed vibration of the single-cylinder steam turbine rotor can be improved by implementing dynamic balancing weighting on the steam-generator coupling without opening the cylinder, thereby improving the efficiency of single-cylinder steam turbine vibration processing and saving costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] The accompanying drawings, which constitute part of the present invention, are intended to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are intended to explain the present invention and do not constitute an undue limitation of the present invention. In the accompanying drawings:

[0043] Figure 1This is a schematic diagram of the installation position of the relative axis vibration sensor;

[0044] Figure 2 This is a simplified structural diagram of the shaft system in Example 2. DETAILED DESCRIPTION

[0045] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of them. All other embodiments obtained by ordinary technicians in this field based on the embodiments of the present invention without making any creative efforts shall fall within the scope of protection of the present invention.

[0046] In the description of the present invention, it is to be understood that the terms “include” and “comprise” indicate the presence of the described features, wholes, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, wholes, steps, operations, elements, components and / or collections thereof.

[0047] It should also be understood that the terms used in the present specification are only for the purpose of describing particular embodiments and are not intended to limit the present invention. As used in the present specification and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms unless the context clearly indicates otherwise.

[0048] It should be further understood that the term "and / or" as used in the present specification and the appended claims refers to and includes any and all possible combinations of one or more of the associated listed items. For example, A and / or B may represent: A exists alone, A and B exist simultaneously, and B exists alone. In addition, the character " / " in the present invention generally indicates that the associated objects are in an "or" relationship.

[0049] It should be understood that although the terms "first," "second," and "third" may be used to describe preset ranges in embodiments of the present invention, these preset ranges should not be limited to these terms. These terms are merely used to distinguish one preset range from another. For example, without departing from the scope of embodiments of the present invention, the first preset range may also be referred to as the second preset range, and similarly, the second preset range may also be referred to as the first preset range.

[0050] The word "if," as used herein, may be interpreted as "at the time of" or "when" or "in response to determining" or "in response to detecting," depending on the context. Similarly, the phrases "if it is determined" or "if (stated condition or event) is detected" may be interpreted as "when it is determined" or "in response to the determination" or "when detecting (stated condition or event)" or "in response to detecting (stated condition or event)," depending on the context.

[0051] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Generally, the components of the embodiments of the present invention described and shown in the drawings herein can be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present invention provided in the drawings is not intended to limit the scope of the claimed invention, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0052] The accompanying drawings illustrate various schematic diagrams of structures according to embodiments disclosed herein. These figures are not drawn to scale; for clarity, some details are exaggerated and some details may be omitted. The shapes of the various regions and layers shown in the figures, as well as their relative sizes and positional relationships, are merely exemplary and may deviate in practice due to manufacturing tolerances or technical limitations. Those skilled in the art may design regions / layers with different shapes, sizes, and relative positions as needed.

[0053] Example 1

[0054] The method for dynamic balancing of critical speed vibration of a single-cylinder steam turbine rotor according to the present invention comprises the following steps:

[0055] 1) Determine the rotation direction of the single-cylinder steam turbine generator set;

[0056] 2) Obtaining the actual installation position information of the key phase sensor and relative shaft vibration sensor of the rotating equipment under test;

[0057] 3) connecting the key phase sensor and relative shaft vibration sensor of the measured rotating equipment to a data acquisition and analysis instrument;

[0058] 4) During the start-up and shutdown of the steam turbine generator set, the data acquisition and analysis instrument obtains relative shaft vibration data at the front and rear bearings of the steam turbine rotor at the critical speed through the key phase sensor and the relative shaft vibration sensor; and simultaneously records the relative shaft vibration data at the front and rear bearings of the generator rotor at the critical speed;

[0059] 5) Based on the relative axial vibration data at the front and rear bearings of the steam turbine rotor and the relative axial vibration data at the front and rear bearings of the generator rotor obtained in step 4), determine whether the phase angle differences of the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor are all ≤ 90°. If the above conditions are met, determine the test weight and test angle, and apply the test weight to the steam-generator coupling; otherwise, dynamic balancing is not recommended.

[0060] 6) Determine the dynamic balance influence coefficient based on the vibration vector before and after weighting and the weighting vector;

[0061] 7) Using the dynamic balance influence coefficient, a relationship between the vibration vector, the dynamic balance influence coefficient, and the weighting vector at the critical speed of the single-cylinder steam turbine rotor is established, and the ideal point method is used to obtain the final weighting vector so that the residual vibration at the critical speed of the single-cylinder steam turbine rotor is minimized.

[0062] In step 1), the rotation direction is the rotation direction of the rotor from the steam turbine to the generator.

[0063] The specific process of step 2) is:

[0064] 21) Measure the angle θ formed between the actual installation position of the key phase sensor and the horizontal or vertical midpoint plane;

[0065] 22) Measure the angle between the relative axis vibration sensor and the key phase sensor actually installed on the left side. Measure the angle between the relative shaft vibration sensor and the key phase sensor actually installed on the right side

[0066] The process of step 3) is:

[0067] Vibration monitoring software is used, along with wavelet transform and spectrum refinement analysis algorithms, to decompose the collected signals into different frequency components, locate the critical speed, and control the error within ±5r / min. Simultaneously, a three-dimensional vibration spectrum is generated in real time to intuitively present how the vibration amplitude, frequency, and phase change with speed.

[0068] The specific process of step 4) is:

[0069] 41) The original relative shaft vibration vector, amplitude and phase angle of the front and rear bearings of the turbine rotor at the critical speed are measured by the data acquisition and analysis instrument.

[0070] 42) The original relative axis vibration vector, amplitude and phase angle of the generator rotor front and rear bearings at the critical speed are measured by a data acquisition analyzer.

[0071] The process of step 5) is:

[0072] When the condition is met: |β c后 -β c前 |≤90° and |β c后 -γ c前 |≤90°

[0073] The applied weight vector and its magnitude and phase angle are:

[0074] According to the original phase, using the formula δ s =β c ±φ+180°-ζ, obtain the test weight angle, where β c is the original phase angle of the front or rear bearing of the turbine rotor, φ is the angle between the relative shaft vibration probe and the key phase probe of the turbine generator set, and ζ is the mechanical hysteresis angle.

[0075] When the rotation direction from the relative shaft vibration sensor to the key phase sensor is consistent with the rotor rotation direction, take +; when the rotation direction from the relative shaft vibration sensor to the key phase sensor is inconsistent with the rotor rotation direction, take -; the mechanical hysteresis angle is 80°~90°.

[0076] Use the following formula to calculate the trial weight M s , where α s is the empirical sensitivity coefficient, which is taken as 400 μm / kg.

[0077]

[0078] When |β c后 -β c前 |>90° or |β c后 -γ c前 |>90°, dynamic balancing is not recommended.

[0079] The dynamic balance influence coefficient in step 6) is:

[0080]

[0081] in, is a vector operator, called the dynamic balance influence coefficient, is the vibration vector of the turbine rotor before weighting, is the vibration vector of the turbine rotor after weighting, is the trial weight vector.

[0082] The operation process of step 7) is:

[0083] During the start-up and shutdown process of the steam turbine generator set, the original relative shaft vibration vectors at the critical speed of the steam turbine rotor are: The corresponding ideal weight vectors are recorded as: The ideal point method is used, that is, by minimizing the Euclidean distance d M and d δ , find the optimal value of weight addition and obtain the final weight addition vector The corresponding amplitude and angle are M and δ respectively, which minimize the residual vibration vector at the critical speed of the single-cylinder steam turbine rotor.

[0084]

[0085] The ideal weight of each measuring point can be obtained from the above formula: M Tc前ideal 、M Tc后ideal 、M Gc前ideal And the corresponding ideal weighting angle: δ Tc前ideal , δ Tc后ideal , δ Gc前ideal .

[0086]

[0087] Where n is the number of vibration measurement points of interest.

[0088] Example 2

[0089] This embodiment takes the critical speed vibration problem of a single-cylinder steam turbine rotor in a power plant as an example to introduce the detailed implementation process of the present invention, thereby illustrating the effectiveness and practicality of the present invention.

[0090] The steam turbine of the No. B steam turbine generator unit in a power plant is a CZZK25-8.83 / 4.1 / (0.6) high-pressure, single-cylinder, extraction, injection, impulse direct air-cooled steam turbine, equipped with a QFW-30-2A air-cooled generator. The unit's shaft system consists of a steam turbine rotor and a generator rotor, and the shaft system is supported by four bearings. The shaft system structure diagram is as follows: Figure 2 shown.

[0091] The unit underwent a Class A overhaul from August to September 2024, during which comprehensive testing of the unit's shafting vibration was conducted. During startup through critical speed after the overhaul, relative shaft vibration at the #2 bearing severely exceeded the specified value, reaching a maximum value of 242 μm. This prevented the unit from maintaining a constant speed of 3,000 rpm. Dynamic balancing and weighting of the turbine-generator coupling were performed on-site, successfully improving the vibration at the #2 bearing at critical speed.

[0092] The specific implementation steps of this embodiment are:

[0093] 1) Determine the rotation direction of the rotating equipment;

[0094] The direction of rotation is determined by looking from the turbine towards the generator. The direction of rotation is determined to be clockwise on site. Figure 1 As shown in ω.

[0095] 2) Obtaining the actual installation position information of the key phase sensor and the relative shaft vibration sensor of the rotating equipment under test;

[0096] Key phase sensor is Figure 1 The position of the Key in the left relative axis vibration sensor is Figure 1 The X in the middle is located, and the right relative axis vibration sensor is Figure 1 The position of Y in the middle,

[0097] 21) The angle θ formed by the key phase sensor and the vertical mid-plane is 0°;

[0098] 22) The angle formed by the left relative axis vibration sensor X and the key phase sensor is The angle formed by the right relative axis vibration sensor Y and the key phase sensor is

[0099] 3) External vibration data acquisition and spectrum analysis instrument;

[0100] Connect the vibration test instrument, that is, connect the relative shaft vibration signal and key phase signal from the buffer output terminal (BUF terminal) of the TSI system to the vibration data acquisition and spectrum analysis instrument. The relative shaft vibration data required for subsequent tests are obtained through this data acquisition and analyzer. The front and rear bearings of the turbine are #1 bearing and #2 bearing respectively, and the front and rear bearings of the generator are #3 bearing and #4 bearing respectively.

[0101] 4) During the start-up and shutdown of the steam turbine generator set, the relative shaft vibration data of the front and rear bearings of the steam turbine rotor at the critical speed is measured by a data acquisition and analysis instrument; at the same time, the relative shaft vibration data of the front and rear bearings of the generator rotor at the critical speed is recorded;

[0102] 41) The original relative shaft vibration vector, amplitude and phase angle at the front and rear bearings of the turbine rotor at the critical speed of the turbine rotor are:

[0103]

[0104] 42) The original relative shaft vibration vector, amplitude and phase angle at the front and rear bearings of the generator rotor at the critical speed of the turbine rotor are:

[0105]

[0106] 5) Using the phase angles obtained in step 4), determine whether the phase angle differences between the front and rear bearings of the turbine rotor and the front bearing of the generator rotor are all less than 90°. If so, determine the test weight and angle, and apply the test weight to the turbine-generator coupling. Otherwise, dynamic balancing is not recommended.

[0107] |131°-206°|=75°<90° and |131°-182°|=51°<90°

[0108] The test weight angle is:

[0109]

[0110] Depend on Figure 1 It can be seen that the rotation direction from the X-relative axis vibration sensor to the key phase sensor is inconsistent with the rotor rotation direction, so - is taken, and the mechanical hysteresis angle ζ is taken as 80°.

[0111] Calculate the test weight angle δ s =131°-135°+180°-90°=86°;

[0112] Calculate the trial weight

[0113] The dynamic balancing test weight vector is: (Unit: g / °).

[0114] 6) According to the vibration vector before and after weighting and the trial weighting vector, determine the dynamic balance influence coefficient. The vibration vector of the 1X and 1Y relative axes after dynamic balance weighting is:

[0115]

[0116] After dynamic balancing, the relative axis vibration vectors of 2X and 2Y are:

[0117]

[0118]

[0119] After dynamic balancing, the relative axis vibration vectors of 3X and 3Y are:

[0120]

[0121] 7) Using the obtained dynamic balance influence coefficient, the relationship between the vibration vector, dynamic balance influence coefficient, and weighting vector at the critical speed of the single-cylinder steam turbine rotor is established; the ideal point method is used to obtain the final weighting vector to minimize the residual vibration at the critical speed of the single-cylinder steam turbine rotor.

[0122] During the start-up and shutdown process of the steam turbine generator set, the original relative shaft vibration vectors at the critical speed of the turbine rotor are: The corresponding ideal added weights are recorded as follows: The ideal point method is used, that is, by minimizing the Euclidean distance d M and d δ To find the optimal value of the weight increase, so as to obtain the final weight increase vector Minimize the residual vibration of the single-cylinder steam turbine rotor at the critical speed.

[0123]

[0124] The ideal weights of each measuring point are calculated from the above formula:

[0125] M 1Xideal =1008g, M 2Xideal =1180g, M 3Xideal =826 grams

[0126] δ 1Xideal =43°, δ 2Xideal =80°,δ 3Xideal =45°

[0127]

[0128] Calculated M = 1004 g;

[0129]

[0130] Calculate d δ =56°.

[0131] The final weighting vector is:

[0132] At this point, the final weight vector of the on-site dynamic balance of the single-cylinder steam turbine rotor at the critical speed vibration is obtained, which can be implemented again when the unit is adjusted, thereby further reducing the residual vibration of the single-cylinder steam turbine rotor at the critical speed.

[0133] Example 3

[0134] The dynamic balancing system for critical speed vibration of a single-cylinder steam turbine rotor according to the present invention comprises:

[0135] a first judgment module, configured to judge whether it is necessary to implement weighting on the steam-generator coupling, and if it is necessary to implement weighting on the steam-generator coupling, implement weighting on the steam-generator coupling;

[0136] A first determining module is used to determine a dynamic balance influence coefficient based on the vibration vector and the weighting vector of the steam turbine rotor before and after weighting is implemented;

[0137] The balancing module is used to establish the relationship between the vibration vector, dynamic balance influence coefficient and weighting vector at the critical speed of the single-cylinder steam turbine rotor according to the dynamic balance influence coefficient, adopt the ideal point method to obtain the final weighting vector, and perform dynamic balancing of the critical speed vibration of the single-cylinder steam turbine rotor according to the final weighting vector.

[0138] In this embodiment, the first judgment module includes:

[0139] The second determining module is used to determine the rotation direction of the single-cylinder steam turbine generator set;

[0140] An acquisition module is used to obtain the actual installation position information of the key phase sensor and the relative shaft vibration sensor of the rotating equipment under test;

[0141] The detection module is used to obtain relative shaft vibration data of the front and rear bearings of the steam turbine rotor at the critical speed through the key phase sensor and the relative shaft vibration sensor during the start-up and shutdown process of the steam turbine generator set; and simultaneously record the relative shaft vibration data of the front and rear bearings of the generator rotor at the critical speed;

[0142] The second judgment module is used to judge whether the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90° based on the relative shaft vibration data at the front and rear bearings of the steam turbine rotor and the relative shaft vibration data at the front and rear bearings of the generator rotor. When the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°, weighting is applied to the steam-generator coupling.

[0143] In this embodiment, the final weight vector is:

[0144]

[0145] Get the ideal weight of each measuring point: M Tc前ideal 、M Tc后ideal 、M Gc前ideal And the corresponding ideal weighting angle: δ Tc前ideal , δ Tc后ideal , δ Gc前ideal .

[0146] The division of modules in the embodiments of the present application is illustrative and is merely a logical functional division. In actual implementation, other division methods may be used. Furthermore, the functional modules in the various embodiments of the present application may be integrated into a single processor, or may exist physically separately, or two or more modules may be integrated into a single module. The aforementioned integrated modules may be implemented in the form of hardware or software functional modules.

[0147] Example 4

[0148] A computer device comprises a memory, a processor, and a computer program stored in the memory and executable on the processor. When the processor executes the computer program, the steps of a method for dynamic balancing of the critical speed vibration of a single-cylinder steam turbine rotor are implemented, for example, including: determining whether weighting is required on a steam-generator coupling, and if weighting is required on the steam-generator coupling, weighting is implemented on the steam-generator coupling; determining a dynamic balancing influence coefficient based on the vibration vector and weighting vector of the steam turbine rotor before and after weighting is implemented; establishing a relationship between the vibration vector, dynamic balancing influence coefficient, and weighting vector at the critical speed of the single-cylinder steam turbine rotor based on the dynamic balancing influence coefficient, obtaining a final weighting vector using an ideal point method, and performing dynamic balancing of the critical speed vibration of the single-cylinder steam turbine rotor based on the final weighting vector. The memory may include internal memory, such as high-speed random access memory, and may also include non-volatile memory, such as at least one disk storage device. The processor, network interface, and memory are interconnected via an internal bus. This internal bus may be an Industry Standard Architecture bus, a Peripheral Component Interconnect Standard bus, an Extended Industry Standard Architecture bus, etc. The bus can be divided into an address bus, a data bus, a control bus, etc. The memory is used to store programs. Specifically, the program may include program code, and the program code includes computer operating instructions. The memory may include internal memory and non-volatile memory, and provides instructions and data to the processor.

[0149] Example 5

[0150] A computer-readable storage medium stores a computer program. When executed by a processor, the computer program implements the steps of a method for dynamic balancing of critical speed vibration of a single-cylinder steam turbine rotor. For example, the method includes: determining whether weighting is required on the steam-generator coupling; if weighting is required, weighting is applied to the steam-generator coupling; determining a dynamic balancing influence coefficient based on the vibration vector and weighting vector of the steam turbine rotor before and after weighting; establishing a relationship between the vibration vector, dynamic balancing influence coefficient, and weighting vector at the critical speed of the single-cylinder steam turbine rotor based on the dynamic balancing influence coefficient; obtaining a final weighting vector using an ideal point method; and performing dynamic balancing of the critical speed vibration of the single-cylinder steam turbine rotor based on the final weighting vector. Specifically, the computer-readable storage medium includes, but is not limited to, volatile memory and / or non-volatile memory. The volatile memory may include random access memory (RAM) and / or cache memory. The non-volatile memory may include read-only memory (ROM), a hard disk, a flash memory, an optical disk, a magnetic disk, etc.

[0151] Those skilled in the art will appreciate that the embodiments of the present application can be provided as methods, systems, or computer program products. Therefore, the present application can adopt the form of a complete hardware embodiment, a complete software embodiment, or an embodiment in combination with software and hardware. Moreover, the present application can adopt the form of a computer program product implemented on one or more computer-usable storage media (including but not limited to magnetic disk storage, CD-ROM, optical storage, etc.) that contain computer-usable program code.

[0152] The present application is described with reference to the flowcharts and / or block diagrams of the methods, devices (systems), and computer program products according to the embodiments of the present application. It should be understood that each process and / or box in the flowchart and / or block diagram, as well as the combination of the processes and / or boxes in the flowchart and / or block diagram, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing device to produce a machine, so that the instructions executed by the processor of the computer or other programmable data processing device generate instructions for implementing the steps in the process. Figure 1 a process or multiple processes and / or boxes Figure 1 A device that provides the functions specified in a block or multiple blocks.

[0153] These computer program instructions may also be stored in a computer readable memory that can direct a computer or other programmable data processing device to work in a specific manner, so that the instructions stored in the computer readable memory produce an article of manufacture comprising an instruction device, which implements the process Figure 1 a process or multiple processes and / or boxes Figure 1 The function specified in one or more boxes.

[0154] These computer program instructions can also be loaded onto a computer or other programmable data processing device so that a series of operational steps are executed on the computer or other programmable device to produce a computer-implemented process, thereby providing the instructions executed on the computer or other programmable device for implementing the process. Figure 1 a process or multiple processes and / or boxes Figure 1 A step that specifies a function in one or more boxes.

[0155] Those skilled in the art will readily identify other embodiments of the present invention after considering the specification and disclosure of the invention. This application is intended to cover any variations, uses, or adaptations of the present invention that follow the general principles of the invention and include common knowledge or customary techniques in the art not disclosed herein. The description and examples are to be considered as exemplary only, with the true scope and spirit of the invention being indicated by the following claims.

[0156] It should be understood that the present invention is not limited to the exact construction described above and shown in the drawings, and that various modifications and changes may be made without departing from the scope thereof. The scope of the present invention is limited only by the appended claims.

[0157] The above description is only a preferred embodiment of the present invention and does not limit the present invention in any way. Any simple modification, change and equivalent structural change made to the above embodiment based on the technical essence of the present invention shall still fall within the scope of protection of the technical solution of the present invention.

Claims

1. A dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor, characterized in that: The following steps are involved: Determine whether it is necessary to add weight to the steam-generator coupling, and if so, add weight to the steam-generator coupling; Determine the dynamic balance influence coefficient based on the vibration vector and weighting vector of the steam turbine rotor before and after weighting; According to the dynamic balance influence coefficient, the relationship between the vibration vector, dynamic balance influence coefficient and weighting vector at the critical speed of the single-cylinder steam turbine rotor is established, the ideal point method is used to obtain the final weighting vector, and the dynamic balance of the critical speed vibration of the single-cylinder steam turbine rotor is performed according to the final weighting vector.

2. The dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to claim 1, characterized in that: The process of determining whether weighting is required on the steam-generator coupling is as follows: Determine the rotation direction of a single-cylinder steam turbine generator set; Obtain the actual installation position information of the key phase sensor and relative shaft vibration sensor of the rotating equipment under test; During the start-up and shutdown of the steam turbine generator set, relative shaft vibration data of the front and rear bearings of the steam turbine rotor at the critical speed are measured by the key phase sensor and the relative shaft vibration sensor; and the relative shaft vibration data of the front and rear bearings of the generator rotor at the critical speed are recorded at the same time; Based on the relative shaft vibration data at the front and rear bearings of the steam turbine rotor and the relative shaft vibration data at the front and rear bearings of the generator rotor, determine whether the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°. When the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°, weighting is applied to the steam-generator coupling.

3. The dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to claim 1, characterized in that: The dynamic balance influence coefficient is: in, is a vector operator, called the dynamic balance influence coefficient, is the vibration vector of the turbine rotor before weighting, is the vibration vector of the turbine rotor after weighting, is the trial weight vector.

4. The dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to claim 3, characterized in that: The final weight vector is: Get the ideal weight of each measuring point: M Tc前ideal 、M Tc后ideal 、M Gc前ldeal And the corresponding ideal weighting angle: δ Tc前ideal , δ Tc后ideal , δ Gc前ideal .

5. The dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to claim 1, characterized in that: The process of obtaining the actual installation position information of the key phase sensor and the relative shaft vibration sensor of the measured rotating equipment is as follows: Measure the angle θ formed between the actual installation position of the key phase sensor and the horizontal or vertical midpoint plane; Measure the angle between the relative shaft vibration sensor and the key phase sensor actually installed on the left side Measure the angle between the relative shaft vibration sensor and the key phase sensor actually installed on the right side 6. A dynamic balancing system for critical speed vibration of a single-cylinder steam turbine rotor, characterized in that: include: a first judgment module, configured to judge whether it is necessary to implement weighting on the steam-generator coupling, and if it is necessary to implement weighting on the steam-generator coupling, implement weighting on the steam-generator coupling; A first determining module is used to determine a dynamic balance influence coefficient based on the vibration vector and the weighting vector of the steam turbine rotor before and after weighting is implemented; The balancing module is used to establish the relationship between the vibration vector, dynamic balance influence coefficient and weighting vector at the critical speed of the single-cylinder steam turbine rotor according to the dynamic balance influence coefficient, adopt the ideal point method to obtain the final weighting vector, and perform dynamic balancing of the critical speed vibration of the single-cylinder steam turbine rotor according to the final weighting vector.

7. The dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to claim 6, characterized in that: The first judgment module includes: The second determining module is used to determine the rotation direction of the single-cylinder steam turbine generator set; An acquisition module is used to obtain the actual installation position information of the key phase sensor and the relative shaft vibration sensor of the rotating equipment under test; The detection module is used to obtain relative shaft vibration data of the front and rear bearings of the steam turbine rotor at the critical speed through the key phase sensor and the relative shaft vibration sensor during the start-up and shutdown process of the steam turbine generator set; and simultaneously record the relative shaft vibration data of the front and rear bearings of the generator rotor at the critical speed; The second judgment module is used to judge whether the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90° based on the relative shaft vibration data at the front and rear bearings of the steam turbine rotor and the relative shaft vibration data at the front and rear bearings of the generator rotor. When the phase angle difference between the front and rear bearings of the steam turbine rotor and the front bearing of the generator rotor is ≤90°, weighting is applied to the steam-generator coupling.

8. The dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor according to claim 6, characterized in that: The final weight vector is: Get the ideal weight of each measuring point: M Tc前ideal 、M Tc后ideal 、M Gc前ideal And the corresponding ideal weighting angle: δ Tc前ideal , δ Tc后ideal , δ Gc前ideal .

9. A computer device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein: When the processor executes the computer program, the steps of the dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor as described in any one of claims 1 to 5 are implemented.

10. A computer-readable storage medium storing a computer program, characterized in that: When the computer program is executed by a processor, the steps of the dynamic balancing method for critical speed vibration of a single-cylinder steam turbine rotor as described in any one of claims 1 to 5 are implemented.

Images