Guide bearing dynamic characteristic coefficient inversion method and device based on strain measurement

Abstract

The invention relates to the technical field of generator sets, and discloses a guide bearing dynamic characteristic coefficient inversion method based on strain measurement, and the method is characterized in that the method comprises the steps: collecting the strain measurement data of a strain gauge array which is disposed on each support arm of a rack provided with a guide bearing, and the strain gauge array has a temperature compensation function; calculating a radial load of the guide bearing based on the strain measurement data; and inverting the dynamic characteristic coefficient of the guide bearing according to the radial load. Therefore, normal operation of a unit on which the guide bearing acts does not need to be interfered, inversion of the dynamic characteristic coefficient of the guide bearing is achieved in combination with the strain measurement data of the guide bearing, the principle is simple, universality is achieved, the method is very suitable for monitoring the bearing characteristic of the guide bearing of a hydroelectric generating set, and the safety of the monitoring process is effectively improved. A guide bearing does not need to be modified, unit performance is not affected, and economical efficiency is good.

Description

Technical Field

[0001] The present invention relates to the technical field of generator sets, and in particular to a method and device for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement. Background Art

[0002] Guide bearings are crucial components of hydroelectric generators. Their primary function is to withstand radial mechanical, electromagnetic, and hydraulic imbalances from the generator's rotating components, maintaining stable operation of the generator's main shaft within the bearing clearance range. Guide bearings are categorized by their support location as upper guide bearings, lower guide bearings, and water-guide bearings. Statistics show that nearly 40% of motor failures are related to guide bearing failures. For example, high radial forces on guide bearings can lead to guide bearing damage and even rotor failure.

[0003] Existing condition monitoring systems for hydropower units typically focus on measuring shaft runout and frame vibration, while ignoring the effects of radial loads on the unit's shafting and rotor. Radial loads acting on hydropower units can be categorized as dynamic and static. Static loads are primarily caused by unbalanced magnetic pull due to stator and rotor eccentricity, shaft clamping due to bearing misalignment, and asymmetric flow characteristics within the turbine. Dynamic loads arise from mechanical unbalance forces caused by rotor imbalance, shape deviations of the generator's stator and rotor, and unstable flow within the turbine. Vibration monitoring in existing on-site condition monitoring systems for power plants only monitors bearing seat acceleration or displacement and fails to measure static loads acting on the unit. Furthermore, estimating the magnitude of dynamic loads based on acceleration or displacement requires first determining the stiffness of the bearing frame and its interconnections. However, the bearing frame typically consists of large steel beams, whose geometry varies with temperature. Generator temperatures range from 15°C to 80°C. Consequently, thermal expansion of the steel beams affects bearing clearances, altering the relationship between bearing performance and radial displacement.

[0004] Therefore, it is necessary to reasonably monitor the radial loads acting on the hydropower unit, which can be divided into dynamic loads and static loads. In the related art, the advantage of the load sensor installed behind the bearing seat is that a suitable load range can be selected for the sensor, and the disadvantage is that it will lead to a decrease in the total radial stiffness. In addition, in the design of hydropower units, numerical simulations or safety margins reserved in the design stage are often used to ensure that the guide bearings have sufficient load-bearing performance. The on-site status monitoring system used in operation and maintenance is not equipped with monitoring and measurement functions for the radial loads of the guide bearings. However, changes in the dynamic behavior of hydropower units are usually caused by changes in the forces acting on the rotor or changes in the dynamic characteristic coefficients of the guide bearings. Therefore, how to accurately grasp the dynamic characteristic coefficients of the guide bearings has become a technical problem that needs to be solved urgently, which is of great significance for ensuring the health of the rotor. Summary of the Invention

[0005] In view of this, the present invention provides a method and device for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement, so as to solve the technical problem of how to accurately grasp the dynamic characteristic coefficient of the guide bearing, which has become an urgent problem to be solved.

[0006] In a first aspect, the present invention provides a method for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement, the method comprising:

[0007] Collect strain measurement data from a strain gauge array installed on each arm of the frame where the guide bearings are installed. The strain gauge array has a temperature compensation function.

[0008] Calculate the radial load of the guide bearing based on the strain measurement data;

[0009] Based on the radial load, the dynamic characteristic coefficient of the guide bearing is inverted.

[0010] The present invention utilizes a strain measurement-based guide bearing dynamic characteristic coefficient inversion method. The method collects strain measurement data from a strain gauge array located on each arm of the frame on which the guide bearing is mounted. The strain gauge array has a temperature compensation function. Based on the strain measurement data, the radial load of the guide bearing is calculated. Based on the radial load, the guide bearing dynamic characteristic coefficient is inverted. This method eliminates the need to interfere with the normal operation of the unit supported by the guide bearing. By combining the guide bearing's strain measurement data, the guide bearing dynamic characteristic coefficient can be inverted. The method utilizes a simple principle and possesses universal applicability, making it highly suitable for monitoring the load characteristics of guide bearings in hydropower units, effectively improving the safety of the monitoring process. Furthermore, the method eliminates the need for guide bearing modification, does not affect unit performance, and offers excellent economic benefits.

[0011] In some optional embodiments, before collecting strain measurement data of the strain gauge array disposed on each support arm of the frame on which the guide bearing is mounted, the method further includes:

[0012] Configuring acquisition system parameters for collecting strain measurement data from a strain gauge array disposed on each arm of the frame on which the guide bearing is mounted;

[0013] The acquisition system parameters include: the resistance temperature coefficient of the strain gauge included in the strain gauge array, the sensitivity coefficient of the strain gauge, the linear expansion coefficient of the strain gauge, and the linear expansion coefficient of the support arm.

[0014] In some optional implementations, the acquisition system parameters meet the following preset constraints:

[0015]

[0016] α0=-K0(β g -β s );

[0017] ΔR t =Rt -R0;

[0018] Among them, R t It represents the resistance value of the strain gauges included in the strain gauge array at the resistance temperature t;

[0019] R0 represents the resistance value of the strain gauge when the resistance temperature is t0;

[0020] α0 represents the temperature coefficient of resistance;

[0021] K0 represents the sensitivity coefficient;

[0022] β s Indicates the linear expansion coefficient of the strain gauge;

[0023] β g Indicates the linear expansion coefficient of the arm.

[0024] In some optional embodiments, the temperature compensation function of the strain gauge array is implemented using a line compensation method of a Wheatstone bridge structure, where two strain gauges of the Wheatstone bridge structure are used to measure the mechanical strain of the support arm, and the other two strain gauges are used for temperature compensation.

[0025] In some optional embodiments, calculating the radial load of the guide bearing based on the strain measurement data includes: calculating the radial load of the guide bearing using the following formula:

[0026]

[0027] Among them, f x 、f y Respectively represent the components of the radial load of the guide bearing in the X and Y directions;

[0028] represents the oil film stiffness matrix of the guide bearing;

[0029] represents the oil film damping matrix of the guide bearing;

[0030] u x 、u y represents the displacement vector component of the guide bearing;

[0031] Represents the velocity vector component of the guide bearing.

[0032] In some optional embodiments, the dynamic characteristic coefficient of the guide bearing is inverted according to the radial load, including:

[0033] Collect the strain measurement data of the guide bearings acting on the rotating shaft of the unit rotor during a set number of complete rotation cycles of the unit rotor using the guide bearings;

[0034] Based on the strain measurement data, determine the force exerted by the guide bearing on the rotating shaft of the unit rotor;

[0035] According to the force of the guide bearing acting on the rotating shaft of the unit rotor, the dynamic characteristic coefficient of the guide bearing is inversely calculated.

[0036] In some optional implementations, the force exerted by the guide bearing on the rotating shaft of the unit rotor is determined based on the strain measurement data using the following formula:

[0037] f s =Tp;

[0038]

[0039]

[0040] Among them, f s Represents the force vector of the guide bearing acting on the rotating shaft of the unit rotor;

[0041] T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing;

[0042] p represents the guide bearing dynamic characteristic coefficient vector.

[0043] In some optional implementations, the dynamic characteristic coefficient of the guide bearing is inversely calculated based on the force exerted by the guide bearing on the rotating shaft of the unit rotor:

[0044] p=T -1 f s ;

[0045] Among them, f s Represents the force vector of the guide bearing acting on the rotating shaft of the unit rotor;

[0046] T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing;

[0047] p represents the dynamic characteristic coefficient vector of the guide bearing.

[0048] In a second aspect, the present invention provides a device for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement, the device comprising:

[0049] An acquisition module is used to collect strain measurement data from a strain gauge array arranged on each arm of the frame on which the guide bearing is installed. The strain gauge array has a temperature compensation function;

[0050] A calculation module for calculating the radial load of the guide bearing based on the strain measurement data;

[0051] The inversion module is used to inverse the characteristic coefficients of the guide bearing dynamics based on the radial load.

[0052] In a third aspect, the present invention provides a computer device comprising: a memory and a processor, the memory and the processor being communicatively connected to each other, the memory storing computer instructions, and the processor executing the computer instructions to execute the guide bearing dynamic characteristic coefficient inversion method based on strain measurement of the above-mentioned first aspect or any corresponding embodiment thereof. BRIEF DESCRIPTION OF THE DRAWINGS

[0053] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the specific embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0054] Figure 1 1 is a flow chart of a method for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement according to an embodiment of the present invention;

[0055] Figure 2 2 is a schematic diagram of the bridge compensation principle according to an embodiment of the present invention;

[0056] Figure 3 Schematic diagram of an equivalent model of a guide bearing according to an embodiment of the present invention;

[0057] Figure 4 1 is a schematic diagram of force decomposition of a guide bearing according to an embodiment of the present invention;

[0058] Figure 5 1 is a structural block diagram of a guide bearing dynamic characteristic coefficient inversion device based on strain measurement according to an embodiment of the present invention;

[0059] Figure 6 Schematic diagram of the hardware structure of a computer device according to an embodiment of the present invention. DETAILED DESCRIPTION

[0060] To make the purpose, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying 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. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making creative efforts shall fall within the scope of protection of the present invention.

[0061] To avoid any internal operations such as installing sensors inside the guide bearing, the present invention provides a method and apparatus for inverting the dynamic characteristic coefficients of a guide bearing based on strain measurement. This method uses a strain gauge mounted on a frame to measure the strain data of the guide bearing, and based on the obtained strain data, the dynamic characteristic coefficients of the guide bearing are inverted. This eliminates the need for any internal operations, effectively ensuring the performance of units using guide bearings. Therefore, the strain measurement-based guide bearing dynamic characteristic coefficient inversion method of the present invention can be applied not only to measuring the dynamic characteristic coefficients of guide bearings in conventional hydro-turbine generator sets, but also to other applicable units such as pumped-storage units.

[0062] According to an embodiment of the present invention, an embodiment of a method for inverting the dynamic characteristic coefficients of a guide bearing based on strain measurement is provided. It should be noted that the steps shown in the flowchart of the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions, and although a logical order is shown in the flowchart, in some cases, the steps shown or described can be executed in an order different from that shown here.

[0063] In this embodiment, a method for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement is provided, which can be used for the above-mentioned hydro-generator set or pumped storage unit. Figure 1 FIG. 1 is a flow chart of a method for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement according to an embodiment of the present invention. Figure 1 As shown, the process includes the following steps:

[0064] Step S101 : collecting strain measurement data of a strain gauge array arranged on each support arm of a frame on which a guide bearing is installed, wherein the strain gauge array has a temperature compensation function.

[0065] In some optional embodiments, a strain gauge array may be installed on each arm of the frame where the guide bearing is installed. The temperature compensation function of the strain gauge array can be achieved by using two methods: line compensation and strain gauge self-compensation.

[0066] Specifically, the most commonly used and most effective line compensation method is based on Figure 2 For example, when measuring the index strain of the frame of the guide bearing, the strain gauges can be arranged into a complete Wheatstone bridge, where two strain gauges are used to measure the mechanical strain in the guide bearing's support arms, and the other two strain gauges are used for temperature compensation. Figure 2 As shown, R1 is used to represent the resistance of the working strain gauge, R B Used to characterize the resistance of the compensating stress sheet, the bridge output voltage U o The relationship with the bridge arm parameters is shown in the following formula:

[0067] U o=I(R1R4-R B R3);

[0068] Among them, U o Represents the output voltage of the bridge;

[0069] I represents a constant determined by the bridge arm resistance and the power supply voltage;

[0070] In actual measurement, you can follow R1=R B =R3=R4 selects the bridge arm resistance.

[0071] The working strain gauge R1 is pasted on the surface of each arm of the frame where the guide bearing is installed, and the compensation strain gauge R B Pasted on the compensation block with the same material as the support arm. And only the working strain gauge bears the strain, and the compensation strain gauge R pasted on the compensation block with the same material as the support arm B Not subject to stress changes.

[0072] When the arm is not under strain, due to R1 and R B In a temperature field with the same ambient temperature t, the bridge parameters can be adjusted to achieve balance. At this time, the relationship between U0, I and the resistance of each bridge arm is as follows:

[0073] U o =I(R1R4-R B R3)=0.

[0074] During the guide bearing application, only the working strain gauges of the strain gauge array are subjected to stress changes.

[0075] When only the resistance temperature of the strain gauge increases or decreases by △t, the resistance changes of the two strain gauges due to the same temperature are equal, and the bridge is still in a balanced state.

[0076] Here we explain the resistance temperature of the strain gauge. The strain gauge itself is a resistor. The resistance temperature here can refer to the temperature of the strain gauge itself or the temperature of the environment in which the strain gauge is located. It can be set and monitored according to actual needs.

[0077] The resistance temperature increase or decrease △t can be expressed by the following formula:

[0078] △t=t-t0;

[0079] Where △t represents the value of the resistance temperature increase or decrease of the strain gauge;

[0080] t represents the current temperature;

[0081] t0 represents the temperature before the resistor temperature increases or decreases.

[0082] Therefore, when the bridge is in a balanced state, the following equation can be obtained:

[0083] U o =I[(R1+ΔR 1t )R4-(R B +ΔR Bt )R3]=0;

[0084] Where I is a constant determined by the bridge arm resistance and the power supply voltage.

[0085] ΔR1 represents the resistance change of the working strain gauge;

[0086] ΔR B Indicates the resistance change of the compensation strain gauge.

[0087] If the arm is affected by strain ε at this time, the working strain gauge resistance R1 will have a new increment △R1=R1Kε, while the compensation sheet does not bear strain and therefore does not produce a new increment. At this time, the bridge output voltage can be expressed by the following formula:

[0088] U o =IR1R4Kε;

[0089] Where I is a constant determined by the bridge arm resistance and the power supply voltage.

[0090] K represents the strain sensitivity coefficient;

[0091] ε represents the strain borne by the strain gauge;

[0092] R1 and R4 respectively represent the resistance values ​​of the resistors pre-configured in the bridge, which are pre-configured fixed values.

[0093] From the above formula, we can know that the output voltage U of the bridge is o It is only related to the strain ε of the arm and has nothing to do with the ambient temperature.

[0094] In some optional implementations, the strain gauge self-compensation uses a temperature self-compensating strain gauge, and the strain gauge that has its own temperature compensation function can be used for compensation.

[0095] The relative change in the total resistance of the strain gauge due to temperature change can be calculated using the following formula:

[0096]

[0097] Where, ΔR t =R t -R0;

[0098] Among them, R t It represents the resistance value of the strain gauges included in the strain gauge array at the resistance temperature t;

[0099] R0 represents the resistance value of the strain gauge when the resistance temperature is t0;

[0100] α0 represents the temperature coefficient of resistance;

[0101] K0 represents the sensitivity coefficient;

[0102] β s Indicates the linear expansion coefficient of the strain gauge;

[0103] β g Indicates the linear expansion coefficient of the arm.

[0104] If the stress piece itself is to realize temperature self-compensation, then α0=-K0(β g -β s ).

[0105] Therefore, in some optional embodiments, before the above S101, the acquisition system parameters are pre-configured, and the acquisition system parameters are used to collect strain measurement data of the strain gauge array arranged on each support arm of the frame installed with the guide bearing. The acquisition system parameters may include: the resistance temperature coefficient of the strain gauge included in the strain gauge array, the sensitivity coefficient of the strain gauge, the linear expansion coefficient of the strain gauge and the linear expansion coefficient of the support arm. The configured acquisition system parameters meet the above equation α0=-K0(β g -β s ).

[0106] In some optional embodiments, the wires of the multiple strain gauges of the strain gauge array may be connected to a strain acquisition instrument, and acquisition system parameters may be set so that the strain measurement data is automatically acquired through the strain acquisition instrument.

[0107] Step S102: Calculate the radial load of the guide bearing based on the strain measurement data.

[0108] In some optional embodiments, reference may be made to Figure 3 The equivalent model of the guide bearing is shown in the figure. The radial load of the guide bearing is calculated using the following formula:

[0109]

[0110] Among them, f x 、f y Respectively represent the components of the radial load of the guide bearing in the X and Y directions;

[0111] represents the oil film stiffness matrix of the guide bearing;

[0112] represents the oil film damping matrix of the guide bearing;

[0113] ux 、u y represents the displacement vector component of the guide bearing;

[0114] Represents the velocity vector component of the guide bearing.

[0115] In general, the stiffness matrix is ​​asymmetric, while the damping matrix is ​​symmetric. When the number of guide bearing pads is even, both the stiffness and damping matrices are symmetric. Since the guide bearing is a tilting pad bearing, it has low cross-coupled stiffness and damping, so it can be assumed that k xx =k yy =k,k xy =k yx =0,c xx =c yy =c,c xy =c yx =0.

[0116] Furthermore, based on Figure 4 The force decomposition diagram of the guide bearing shown above expresses the radial load of the guide bearing as follows in polar coordinates:

[0117]

[0118] in, θ is the guide bearing damping force f c and elastic force f k The angle between them, α is the elastic force f of the guide bearing k The angle with the positive X-axis.

[0119] Therefore, the radial load component of the guide bearing acting on the unit can be calculated using the following formula:

[0120]

[0121] Among them, ε i =ε t +ε f ;

[0122] E is the elastic modulus of the guide bearing, A is the cross-sectional area of ​​the support arm, ε i is the measured strain of the support arm, which is the sum of the mechanical strain caused by the force acting on the guide bearing and the thermal strain caused by temperature changes. is the arm angle, n is the number of arms, ε t is the thermal strain of the guide bearing, ε f is the mechanical strain of the guide bearing.

[0123] Assuming the frame is symmetrical and the temperature changes in the arms are equal, the net strain due to the temperature change is zero and the frame strain depends only on the forces acting on the guide bearings.

[0124] Step S103: inversely calculate the dynamic characteristic coefficient of the guide bearing according to the radial load.

[0125] In some optional embodiments, based on the reasoning of step S102 above, the frame strain depends solely on the force acting on the guide bearing. Therefore, during a set number of complete rotation cycles of the generator rotor employing the guide bearing, strain measurement data of the guide bearing acting on the generator rotor shaft is collected. Based on the strain measurement data, the force acting on the generator rotor shaft by the guide bearing is determined. The dynamic characteristic coefficient of the guide bearing can then be inverted based on the force acting on the generator rotor shaft by the guide bearing.

[0126] For example, by measuring three complete rotation cycles of the unit rotor, the force exerted by the guide bearing on the shaft can be expressed in matrix form:

[0127] f s =Tp;

[0128] in,

[0129]

[0130] f s Represents the force vector of the guide bearing acting on the rotating shaft of the unit rotor;

[0131] T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing;

[0132] p represents the dynamic characteristic coefficient vector of the guide bearing.

[0133] Based on , the following formula can be used to obtain the guide bearing dynamic characteristic coefficient vector p:

[0134] p=T -1 f s ;

[0135] The meaning of each parameter is the same as above.

[0136] The present invention utilizes a strain measurement-based guide bearing dynamic characteristic coefficient inversion method. The method collects strain measurement data from a strain gauge array located on each arm of the frame on which the guide bearing is mounted. The strain gauge array has a temperature compensation function. Based on the strain measurement data, the radial load of the guide bearing is calculated. Based on the radial load, the guide bearing dynamic characteristic coefficient is inverted. This method eliminates the need to interfere with the normal operation of the unit supported by the guide bearing. By combining the guide bearing's strain measurement data, the guide bearing dynamic characteristic coefficient can be inverted. The method utilizes a simple principle and is universally applicable, making it ideal for monitoring the load characteristics of guide bearings in hydropower units, effectively improving the safety of the monitoring process. Furthermore, the method eliminates the need to modify the guide bearing, which does not affect unit performance and offers excellent economic benefits.

[0137] This embodiment also provides a device for inverting the dynamic characteristic coefficients of a guide bearing based on strain measurement. This device is used to implement the above-mentioned embodiments and preferred embodiments, and details already described are omitted. As used below, the term "module" may refer to a combination of software and / or hardware that implements a predetermined function. Although the devices described in the following embodiments are preferably implemented in software, implementation using hardware, or a combination of software and hardware, is also possible and contemplated.

[0138] This embodiment provides a guide bearing dynamic characteristic coefficient inversion device based on strain measurement, such as Figure 5 Shown, including:

[0139] An acquisition module 501 is used to collect strain measurement data from a strain gauge array disposed on each arm of the frame on which the guide bearing is mounted, wherein the strain gauge array has a temperature compensation function;

[0140] A calculation module 502 is used to calculate the radial load of the guide bearing based on the strain measurement data;

[0141] The inversion module 503 is used to inversely calculate the characteristic coefficient of the guide bearing dynamics based on the radial load.

[0142] In some optional embodiments, the device further comprises:

[0143] a configuration module for configuring acquisition system parameters before acquiring strain measurement data of the strain gauge arrays arranged on the respective arms of the frame on which the guide bearings are mounted, wherein the acquisition system parameters are used to acquire strain measurement data of the strain gauge arrays arranged on the respective arms of the frame on which the guide bearings are mounted;

[0144] The acquisition system parameters include: the resistance temperature coefficient of the strain gauge included in the strain gauge array, the sensitivity coefficient of the strain gauge, the linear expansion coefficient of the strain gauge, and the linear expansion coefficient of the support arm.

[0145] In some optional implementations, the acquisition system parameters meet the following preset constraints:

[0146]

[0147] α0=-K0(β g -β s );

[0148] ΔR t =R t -R0;

[0149] Among them, R t It represents the resistance value of the strain gauges included in the strain gauge array at the resistance temperature t;

[0150] R0 represents the resistance value of the strain gauge when the resistance temperature is t0;

[0151] α0 represents the temperature coefficient of resistance;

[0152] K0 represents the sensitivity coefficient;

[0153] β s Indicates the linear expansion coefficient of the strain gauge;

[0154] β g Indicates the linear expansion coefficient of the arm.

[0155] In some optional embodiments, the temperature compensation function of the strain gauge array is implemented using a line compensation method of a Wheatstone bridge structure, where two strain gauges of the Wheatstone bridge structure are used to measure the mechanical strain of the support arm, and the other two strain gauges are used for temperature compensation.

[0156] In some optional embodiments, the calculation module includes:

[0157] The first calculation unit is used to calculate the radial load of the guide bearing using the following formula:

[0158]

[0159] Among them, f x 、f y Respectively represent the components of the radial load of the guide bearing in the X and Y directions;

[0160] represents the oil film stiffness matrix of the guide bearing;

[0161] represents the oil film damping matrix of the guide bearing;

[0162] u x 、u y represents the displacement vector component of the guide bearing;

[0163] Represents the velocity vector component of the guide bearing.

[0164] In some optional embodiments, the inversion module 503 includes:

[0165] A periodic acquisition unit for acquiring strain measurement data of the guide bearing acting on the rotating shaft of the unit rotor within a set number of complete rotation cycles of the unit rotor using the guide bearing;

[0166] a determination unit, configured to determine a force exerted by the guide bearing on the rotating shaft of the unit rotor based on the strain measurement data;

[0167] The characteristic unit is used to inversely calculate the dynamic characteristic coefficient of the guide bearing according to the force acting on the rotating shaft of the unit rotor by the guide bearing.

[0168] In some optional embodiments, the characteristic unit uses the following formula to determine the force exerted by the guide bearing on the rotating shaft of the unit rotor based on the strain measurement data:

[0169] f s =Tp;

[0170]

[0171] Among them, f s Represents the force vector of the guide bearing acting on the rotating shaft of the unit rotor;

[0172] T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing;

[0173] p represents the guide bearing dynamic characteristic coefficient vector.

[0174] In some optional implementations, the dynamic characteristic coefficient of the guide bearing is inversely calculated based on the force exerted by the guide bearing on the rotating shaft of the unit rotor:

[0175] p=T -1 f s ;

[0176] Among them, f s Represents the force vector of the guide bearing acting on the rotating shaft of the unit rotor;

[0177] T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing;

[0178] p represents the dynamic characteristic coefficient vector of the guide bearing.

[0179] The further functional description of each of the above modules and units is the same as that of the above corresponding embodiments and will not be repeated here.

[0180] The guide bearing dynamic characteristic coefficient inversion device based on strain measurement in this embodiment is presented in the form of a functional unit, where the unit refers to an ASIC (Application Specific Integrated Circuit) circuit, a processor and memory that executes one or more software or fixed programs, and / or other devices that can provide the above functions.

[0181] The embodiment of the present invention also provides a computer device having the above Figure 5 The guide bearing dynamic characteristic coefficient inversion device based on strain measurement is shown.

[0182] See also Figure 6 , Figure 6 is a structural diagram of a computer device provided by an optional embodiment of the present invention, such as Figure 6 As shown, the computer device includes: one or more processors 10, memory 20, and interfaces for connecting various components, including high-speed interfaces and low-speed interfaces. Various components utilize different buses to communicate with each other and can be installed on a common mainboard or installed in other ways as needed. The processor can process the instructions executed in the computer device, including instructions stored in the memory or on the memory to display the graphical information of the GUI on an external input / output device (such as, a display device coupled to the interface). In some optional embodiments, if necessary, multiple processors and / or multiple buses can be used together with multiple memories and multiple memories. Equally, multiple computer devices can be connected, and each device provides part of the necessary operations (for example, as a server array, a group of blade servers, or a multi-processor system). Figure 6 A processor 10 is taken as an example.

[0183] The processor 10 may be a central processing unit, a network processor, or a combination thereof. The processor 10 may further include a hardware chip. The hardware chip may be an application-specific integrated circuit, a programmable logic device, or a combination thereof. The programmable logic device may be a complex programmable logic device, a field programmable gate array, a general purpose array logic, or any combination thereof.

[0184] The memory 20 stores instructions that can be executed by at least one processor 10, so as to enable at least one processor 10 to execute the method shown in the above embodiment.

[0185] The memory 20 may include a program storage area and a data storage area, wherein the program storage area may store an operating system and application programs required for at least one function; the data storage area may store data created based on the use of the computer device, etc. In addition, the memory 20 may include a high-speed random access memory, and may also include a non-transient memory, such as at least one disk storage device, a flash memory device, or other non-transient solid-state storage device. In some optional embodiments, the memory 20 may optionally include a memory remotely located relative to the processor 10, and these remote memories may be connected to the computer device via a network. Examples of the above-mentioned network include, but are not limited to, the Internet, an intranet, a local area network, a mobile communication network, and combinations thereof.

[0186] The memory 20 may include a volatile memory, such as a random access memory; the memory may also include a non-volatile memory, such as a flash memory, a hard disk or a solid-state drive; the memory 20 may also include a combination of the above types of memory.

[0187] The computer device further includes a communication interface 30 for the computer device to communicate with other devices or a communication network.

[0188] The embodiment of the present invention also provides a computer-readable storage medium. The above-mentioned method according to the embodiment of the present invention can be implemented in hardware, firmware, or implemented as a computer code that can be recorded in a storage medium, or implemented as a computer code that is originally stored in a remote storage medium or a non-temporary machine-readable storage medium and downloaded through a network and will be stored in a local storage medium, so that the method described herein can be stored in such software processing on a storage medium using a general-purpose computer, a dedicated processor, or programmable or dedicated hardware. Among them, the storage medium can be a magnetic disk, an optical disk, a read-only storage memory, a random access memory, a flash memory, a hard disk or a solid-state drive, etc.; further, the storage medium can also include a combination of the above-mentioned types of memory. It can be understood that a computer, a processor, a microprocessor controller or programmable hardware includes a storage component that can store or receive software or computer code. When the software or computer code is accessed and executed by a computer, a processor or hardware, the method shown in the above embodiment is implemented.

[0189] A portion of the present invention may be applied as a computer program product, such as a computer program instruction, which, when executed by a computer, can call or provide the method and / or technical solution according to the present invention through the operation of the computer. Those skilled in the art should understand that the form in which the computer program instruction exists in a computer-readable medium includes, but is not limited to, a source file, an executable file, an installation package file, etc. Accordingly, the way in which the computer program instruction is executed by the computer includes, but is not limited to: the computer directly executes the instruction, or the computer compiles the instruction and then executes the corresponding compiled program, or the computer reads and executes the instruction, or the computer reads and installs the instruction and then executes the corresponding installed program. Here, the computer-readable medium may be any available computer-readable storage medium or communication medium that can be accessed by the computer.

[0190] Although the embodiments of the present invention have been described with reference to the accompanying drawings, those skilled in the art may make various modifications and variations without departing from the spirit and scope of the present invention. Such modifications and variations are all within the scope defined by the appended claims.

Claims

1. A method for inverting the dynamic characteristic coefficient of a guide bearing based on strain measurement, characterized in that: The method comprises: Collecting strain measurement data from a strain gauge array disposed on each arm of the frame on which the guide bearing is mounted, wherein the strain gauge array has a temperature compensation function; calculating the radial load of the guide bearing based on the strain measurement data; The dynamic characteristic coefficient of the guide bearing is inversely calculated based on the radial load.

2. The method according to claim 1, characterized in that Before collecting strain measurement data of the strain gauge arrays arranged on the respective arms of the frame on which the guide bearings are installed, the method further includes: Configuring acquisition system parameters for collecting strain measurement data from a strain gauge array disposed on each arm of a frame on which a guide bearing is mounted; The acquisition system parameters include: the resistance temperature coefficient of the strain gauge included in the strain gauge array, the sensitivity coefficient of the strain gauge, the linear expansion coefficient of the strain gauge, and the linear expansion coefficient of the support arm.

3. The method according to claim 2, characterized in that The acquisition system parameters meet the following preset constraints: α0＝-K0(β g -β s )； ΔR t =R t -R0; Among them, R t represents the resistance value of the strain gauges included in the strain gauge array when the resistance temperature is t; R0 represents the resistance value of the strain gauge when the resistance temperature is t0; α0 represents the temperature coefficient of resistance; K0 represents the sensitivity coefficient; β s represents the linear expansion coefficient of the strain gauge; β g represents the linear expansion coefficient of the arm.

4. The method according to claim 1, wherein The temperature compensation function of the strain gauge array is realized by adopting a line compensation method of a Wheatstone bridge structure, wherein two strain gauges of the Wheatstone bridge structure are used to measure the strain of the support arm, and the other two strain gauges are used for temperature compensation.

5. The method according to claim 1, wherein Calculating the radial load of the guide bearing based on the strain measurement data includes: calculating the radial load of the guide bearing using the following formula: Among them, f x 、f y Respectively represent the components of the radial load of the guide bearing in the X and Y directions; represents the oil film stiffness matrix of the guide bearing; represents the oil film damping matrix of the guide bearing; u x 、u y represents the displacement vector component of the guide bearing; represents the velocity vector component of the guide bearing.

6. The method according to claim 1, wherein The inverse calculation of the dynamic characteristic coefficient of the guide bearing according to the radial load includes: collecting strain measurement data of the guide bearing acting on the rotating shaft of the unit rotor within a set number of complete rotation cycles of the unit rotor using the guide bearing; determining, based on the strain measurement data, a force exerted by the guide bearing on the rotating shaft of the unit rotor; According to the force of the guide bearing acting on the rotating shaft of the unit rotor, the dynamic characteristic coefficient of the guide bearing is inverted.

7. The method according to claim 1, characterized in that The force exerted by the guide bearing on the rotating shaft of the unit rotor is determined based on the strain measurement data using the following formula: f s =Tp; Among them, f s Indicates the force vector of the guide bearing acting on the rotating shaft of the unit rotor; T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing; p represents the guide bearing dynamic characteristic coefficient vector.

8. The method according to claim 1, characterized in that The following formula is used to inversely calculate the dynamic characteristic coefficient of the guide bearing based on the force exerted by the guide bearing on the rotating shaft of the unit rotor: p=T -1 f s ; Among them, f s represents the force vector of the guide bearing acting on the rotating shaft of the unit rotor; T represents the conversion matrix between the force acting on the rotating shaft of the unit rotor by the guide bearing and the dynamic characteristic coefficient vector of the guide bearing; p represents the dynamic characteristic coefficient vector of the guide bearing.

9. A guide bearing dynamic characteristic coefficient inversion device based on strain measurement, characterized in that: The device comprises: An acquisition module, for acquiring strain measurement data from a strain gauge array disposed on each arm of the frame on which the guide bearing is mounted, wherein the strain gauge array has a temperature compensation function; a calculation module, configured to calculate the radial load of the guide bearing based on the strain measurement data; An inversion module is used to invert the characteristic coefficient of the guide bearing dynamics according to the radial load.

10. A computer device, characterized in that: include: A memory and a processor, wherein the memory and the processor are communicatively connected to each other, the memory stores computer instructions, and the processor executes the guide bearing dynamic characteristic coefficient inversion method based on strain measurement according to any one of claims 1 to 8 by executing the computer instructions.

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