CN118013894A - Hydraulic excitation optimization control method based on radial force distribution of pump body - Google Patents
Hydraulic excitation optimization control method based on radial force distribution of pump body Download PDFInfo
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Abstract
The invention provides a hydraulic excitation optimization control method based on pump radial force distribution, which comprises the following steps: according to actual engineering requirements, an initial water pump model selection scheme is formulated; carrying out three-dimensional modeling on the water pump and the engineering environment in the water pump model selection scheme, and carrying out grid division on the established calculation model to obtain a discrete model; performing steady calculation on the discrete model by using computational fluid dynamics software to obtain a static calculation result; based on a static calculation result, performing unsteady calculation on the discrete model by using computational fluid dynamics software; calculating to obtain water pump radial force time domain data; and performing frequency domain conversion on the water pump radial force time domain data, judging a main source of hydraulic excitation according to the water pump radial force frequency domain data, and optimizing aiming at different sources to obtain an optimal vibration reduction scheme. The hydraulic excitation optimization control method based on the radial force distribution of the pump body provided by the invention directly optimizes the vibration analysis of the pump body, is efficient and low in cost, and has strong universality.
Description
Technical Field
The invention belongs to the technical field of water pump control, and particularly relates to a hydraulic excitation optimization control method based on pump radial force distribution.
Background
The pump is an important energy conversion device and fluid conveying equipment, is widely applied to various large water conservancy hubs and pump station engineering, and plays an important role in the stable development of national economy. Vibration occupies a large proportion in pump faults, and is an important factor affecting the safe and stable operation of a unit and even the whole pump station; on the other hand, noise pollution caused by severe vibration is also unfavorable for the health of engineering personnel and the construction of environment-friendly engineering. The source of vibration of the pump unit device is extremely complex, and the pump unit device is the result of the combined action of various factors such as exciting force, mechanical force, structural rigidity, resonance and the like, wherein the action ratio of the fluid exciting force is very large. Therefore, the establishment of an algorithm for optimizing the hydraulic excitation so as to seek an optimal vibration damping scheme has important significance.
Currently, the hydraulic excitation problem of a pump unit is mainly solved by a technical means of combining Computational Fluid Dynamics (CFD) numerical simulation and experiments, and the method usually needs to take a long time period and has high economic cost. Specifically, CFD research which is developed by taking hydraulic excitation as an optimization object, wherein the analysis focus is concentrated on pressure pulsation of different monitoring points in a flow channel, and the simulation method is widely adopted because of a mature theoretical basis and a matched experimental device, but the essence of the simulation method is not to directly perform vibration analysis on a pump body per se, but to reflect the hydraulic excitation condition of the pump body by calculating pressure pulsation data of each point in a flow channel water body and analyzing pulse characteristics. The method is therefore an indirect estimation method, i.e. estimating pump vibration with hydraulic pulses. In addition, experiments on pressure pulsation are also often performed on scaled model pumps, so that the purpose of the scaled model pumps is to enable an experimental model to meet relevant experimental conditions and save experimental cost, and thus large working condition deviation exists between the performed experiments and actual engineering, and the actual engineering situation cannot be accurately reflected. Although some scholars and related enterprises have constructed engineering model experiment devices with equal proportion scaling at the present stage, under the support of similar theory, the consistency of experimental working conditions and actual engineering can be ensured, however, the model device with high cost is applicable to only a single engineering, and has a pushing effect on the research of engineering mechanism and the summary of engineering experience, but has low economic applicability and long time period. How to know the hydraulic excitation characteristics of different water pump projects and establish a scientific and effective vibration optimization flow under lower economic and time cost is a lack of research content.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: the hydraulic excitation optimization control method based on the radial force distribution of the pump body is provided, the vibration analysis of the pump body is directly optimized, and the hydraulic excitation optimization control method is efficient, low in cost and high in universality.
In order to solve the technical problems, the embodiment of the invention provides a hydraulic excitation optimization control method based on pump radial force distribution, which comprises the following steps:
Step 101, an initial water pump model selection scheme is formulated according to actual engineering requirements;
102, carrying out three-dimensional modeling on a water pump and an engineering environment in a water pump model selection scheme, and carrying out grid division on an established calculation model to obtain a discrete model;
Step 103, performing steady calculation on the discrete model by using computational fluid dynamics software to obtain a static calculation result;
104, based on a static calculation result, performing unsteady calculation on the discrete model by using computational fluid dynamics software; in the calculation process, calculating to obtain water pump radial force time domain data through a water pump radial force function;
step 105, performing frequency domain conversion on the water pump radial force time domain data to obtain water pump radial force frequency domain data;
and 106, judging main sources of hydraulic excitation according to the radial force frequency domain data of the water pump, and optimizing aiming at different sources to obtain an optimal vibration reduction scheme.
As a further improvement of the embodiment of the invention, the water pump radial force time domain data comprises radial component force time domain data of the impeller, radial component force time domain data of the guide vane body, radial component force time domain data of the pump body wall surface and water pump radial resultant force time domain data;
In the step 104, before the unsteady calculation is performed, a radial component force function of the hydraulic component of the water pump and a radial resultant force function of the water pump are written in computational fluid dynamics software.
As a further improvement of the embodiment of the invention, the radial component force function of the hydraulic component of the water pump comprises a radial component force function of the impeller shown in the formula (1), a radial component force function of the guide vane body shown in the formula (2) and a radial component force function of the pump body wall surface shown in the formula (3):
(1)
(2)
(3)
The radial resultant force function of the water pump is shown as (4):
(4)
In the method, in the process of the invention,Representing the radial component of the impeller,/>Representing the radial component of the vane body,/>Representing the radial component of the pump body wall surface,/>Representing the radial resultant force of the water pump,/>Representing self-contained radial force functions in computational fluid dynamics software,/>Representing the name of the impeller in the computational model,/>Representing the name of the vane body in the computational model,/>The name of the pump body wall in the calculation model is indicated.
In step 106, the main source of hydraulic excitation is determined according to the radial component force frequency domain data and the radial resultant force frequency domain data of each water pump hydraulic component, and optimization is performed for different sources to obtain an optimal vibration damping scheme of the component force of each water pump hydraulic component and an optimal vibration damping scheme of the resultant force of the water pump.
As a further improvement of the embodiment of the present invention, the step 106 specifically includes:
step 1061, sorting the radial force frequency domain data of the water pump according to the magnitude from large to small to obtain the magnitude of the top 5 bits 、/>、/>、/>And/>5 Frequencies/>, respectively corresponding、/>、/>、/>And/>；
The total energy of vibration is calculated using equation (5):
(5)
Step 1062, if there is a frequency equal to the pump body natural frequency or a frequency less than 5% of the pump body natural frequency difference in the 5 frequencies, re-making a pump model selection scheme, and executing step 102; otherwise, go to step 1063;
Step 1063, if there is a frequency N times greater than the impeller rotation frequency in the 5 frequencies, where N is an integer greater than or equal to 1, optimizing a hydraulic component of the pump in the pump model selection scheme, and executing step 102; otherwise, if the total energy of vibration reaches a minimum or no more change occurs, then step 1064 is performed; otherwise, optimizing the hydraulic component of the main pump in the water pump model selection scheme, and executing step 102;
step 1064, optimizing an engineering runner in the water pump model selection scheme, and executing step 102; if the total vibration energy reaches the minimum value or no change occurs any more, an optimal vibration reduction scheme is obtained; otherwise, the engineering runner in the water pump model selection scheme is optimized, and step 102 is executed.
As a further improvement of the embodiment of the present invention, the step 106 further includes:
Step 1065, calculating the vibration damping total energy of the optimal vibration damping scheme by using the formula (6):
(6)
In the method, in the process of the invention,Represents the total vibration reduction energy of the optimal vibration reduction scheme,/>Representing the total energy of vibration of the initial water pump model selection scheme,/>Representing the total vibration energy of the optimal damping scheme.
As a further improvement of the embodiment of the invention, the method for optimizing the hydraulic component of the water pump in the water pump model selection scheme comprises one or more of adjusting the inlet and outlet setting angles of the impeller blades, adjusting the inlet and outlet setting angles of the guide vane blades, adjusting the distance between the impeller and the guide vane body, adjusting the size of the clearance between the blade tops and adjusting the quantity, the wrap angle and the height of the guide vane blades.
As a further improvement of the embodiment of the invention, the method for optimizing the engineering runner in the water pump model selection scheme comprises one or more of designing an anti-rotation plate in the water inlet runner, adjusting the section transition of the water inlet runner, adjusting the rear wall distance of a pump body shaft, adjusting the section transition of a water suction horn, adjusting the diffusion angle of a guide vane body and adjusting the center radius of a water outlet elbow.
As a further improvement of the embodiment of the present invention, in step 105, frequency domain conversion is performed on the time domain data of the radial force of the water pump of the last 3 circles in the calculation process.
As a further improvement of the embodiment of the present invention, in the step 102, the mesh encryption process is performed on the hydraulic component area of the water pump when the mesh division is performed.
Compared with the prior art, the technical scheme of the invention has the following beneficial effects: according to the hydraulic excitation optimization control method based on pump radial force distribution, radial force function of a hydraulic component of a water pump is written on the basis of establishing a calculation model and a fluid control equation, radial force data of the pump are obtained in the calculation process, frequency domain conversion is carried out on radial force time domain data based on the FFT principle, main sources of hydraulic excitation are judged according to main frequency components, and optimization is carried out on different vibrations. The radial force data obtained by the method can more directly and accurately reflect the vibration amplitude and frequency of different parts, so that the vibration source components can be accurately judged and the direction can be clearly optimized. Compared with a method for realizing vibration reduction by researching a vibration mechanism through a vibration experiment, the method can save a great deal of time cost and economic cost, and directly avoid the problem that an experimental model device is inconsistent with an engineering model. Moreover, the invention has extremely strong universal meaning, is suitable for various different types of water pump system engineering, and can also know what hydraulic excitation characteristics can be generated by adopting different types of water pumps aiming at a certain engineering.
Drawings
FIG. 1 is a flow chart of a hydraulic excitation optimization control method based on pump radial force distribution provided by an embodiment of the invention;
FIG. 2 is a schematic diagram of a computational model built in an embodiment of the present invention;
FIG. 3 is a time domain data diagram in an embodiment of the invention;
fig. 4 is a diagram of frequency domain data in an embodiment of the invention.
Detailed Description
The technical scheme of the invention is described in detail below with reference to the accompanying drawings.
The embodiment of the invention provides a hydraulic excitation optimization control method based on pump radial force distribution, which is shown in fig. 1 and comprises the following steps:
And 101, formulating an initial water pump model selection scheme according to actual engineering requirements.
And 102, carrying out three-dimensional modeling on the water pump and the engineering environment in the water pump model selection scheme, and carrying out grid division on the established calculation model to obtain a discrete model.
And 103, performing steady calculation on the discrete model by using computational fluid dynamics software to obtain a static calculation result.
104, Based on a static calculation result, performing unsteady calculation on the discrete model by using computational fluid dynamics software; in the calculation process, water pump radial force time domain data are obtained through water pump radial force function calculation.
And 105, performing frequency domain conversion on the water pump radial force time domain data to obtain water pump radial force frequency domain data.
And 106, judging main sources of hydraulic excitation according to the radial force frequency domain data of the water pump, and optimizing aiming at different sources to obtain an optimal vibration reduction scheme.
In step 101, an initial water pump model selection scheme is formulated according to an actual engineering environment, wherein the water pump model selection scheme specifically comprises performance parameters such as water pump model, flow, lift, rotation speed and the like of a water pump, a water pump installation mode and the like.
In step 102, a three-dimensional modeling software is adopted to build a calculation model for the water pump model selection scheme and the engineering environment, and grid division software is adopted to discrete the calculation model. Wherein, the established calculation model comprises a pump section area and all flow passage areas of the water pump engineering, and ensures that the calculation model is consistent with the actual engineering environment.
Preferably, when grid division is performed, grid encryption processing is performed on a hydraulic component area (such as a near wall surface, an impeller, a guide vane body and the like) of the water pump and an engineering part so as to ensure the accuracy and the high efficiency of numerical calculation.
In step 103, the discrete model is subjected to steady-state calculation by using computational fluid dynamics software. The impeller area is set to be a rotation area, the rotating speed is the corresponding rated rotating speed of the water pump, and the rest calculation areas are all static areas. Preferably, if the water pump used in the actual engineering is in a centrifugal type, the dynamic and static areas are connected by adopting a Frozen Rotor interface; if the water pump used in the actual engineering is in an axial flow type or mixed flow type, the dynamic and static areas are connected by adopting a stage interface. Setting the total number of step sizes to reach a steady state, wherein the convergence standard of the steady state is that the RMS value of the residual curve is lower than 1.0E-4.
Establishing a fluid control equation, wherein the continuity equation and the momentum equation are respectively as follows:
；
；
In the method, in the process of the invention, Representing the component of the time average velocity in the x direction,/>Representing the component of the time average velocity in the y direction,/>Representing the position component along the x-axis,/>Representing the position component along the y-axis,/>Representing the time-averaged pressure of the fluid,/>Representing fluid density,/>Representing the kinematic viscosity coefficient of a fluid,/>Representing an unknown stress component.
The turbulence model calls a K-Epsilon model, and the expression of a fluid transport equation is as follows:
；
；
；
In the method, in the process of the invention, Representing turbulent energy,/>Representing vortex viscosity coefficient,/>Representing the turbulent kinetic energy generated by the average velocity gradient,Representing the turbulent dissipation ratio,/>Representing turbulent viscosity,/>，/>，/>、/>，。
In step 104, the result file of the constant value calculation in step 103 is used as the initial condition of transient simulation, and the calculation type is set as implicit non-constant. Preferably, the time step calculated in an unsteady manner is set as the time for the impeller to rotate by 3 degrees, and the total calculated time length is the time for the impeller to rotate by 6 circles.
The radial component force function and the radial resultant force function of the water pump hydraulic component are written in computational fluid dynamics software, and are respectively as follows:
(1)
(2)
(3)
(4)
In the method, in the process of the invention,Representing the radial component of the impeller,/>Representing the radial component of the vane body,/>Representing the radial component of the pump body wall surface,/>Representing the radial resultant force of the water pump,/>Representing self-contained radial force functions in computational fluid dynamics software,/>Representing the name of the impeller in the computational model,/>Representing the name of the vane body in the computational model,/>The name of the pump body wall in the calculation model is indicated.
Because the unsteady calculation result is more stable in the later period, preferably, the time domain data of the radial force of the water pump of the last 3 circles in the calculation process is selected for storage, and the storage frequency is set to store the calculation result once for each calculation time step. Thereby obtaining radial component force time domain data of the impeller, radial component force time domain data of the guide vane body, radial component force time domain data of the pump body wall surface and radial resultant force time domain data of the water pump for subsequent processing. The device specifically comprises component force time domain data of an impeller in the x direction, component force time domain data of an impeller in the y direction, component force time domain data of a guide vane body in the x direction, component force time domain data of a pump body wall surface in the y direction, component force time domain data of a resultant force in the x direction and component force time domain data of a resultant force in the y direction.
In step 105, frequency domain conversion is performed on the water pump radial force time domain data of the last 3 circles in the calculation process, so that time-radial force data are converted into frequency-amplitude data, and water pump radial force frequency domain data are obtained.
In particular, the FFT transform principle is adopted, i.e. the assumption is thatIs a finite length sequence of length M, then the spectrumDiscrete values/>Can be calculated as follows:
；
In the method, in the process of the invention, Representing frequency resolution,/>Representing the number of sampling points,/>Representing the sampling time interval.
The method comprises the steps of obtaining component force frequency domain data of an impeller in the x direction, component force frequency domain data of a guide vane body in the y direction, component force frequency domain data of a pump body wall surface in the x direction, component force frequency domain data of a pump body wall surface in the y direction, component force frequency domain data of a resultant force in the x direction and component force frequency domain data of a resultant force in the y direction.
And 106, judging main sources of hydraulic excitation according to the radial component force frequency domain data of the hydraulic components of the water pumps and the radial resultant force frequency domain data of the water pumps, and optimizing the main sources to obtain an optimal vibration reduction scheme of the component force of the hydraulic components of the water pumps and an optimal vibration reduction scheme of the resultant force of the water pumps.
And judging main sources of hydraulic excitation according to the component force frequency domain data of the impeller in the x direction, and optimizing the main sources to obtain an optimal vibration reduction scheme of the impeller in the x direction. The method specifically comprises the following steps:
step 1061, sorting the radial force frequency domain data of the water pump according to the magnitude from large to small to obtain the magnitude of the top 5 bits 、/>、/>、/>And/>5 Frequencies/>, respectively corresponding、/>、/>、/>And/>；
The total energy of vibration is calculated using equation (5):
(5)
Step 1062, if there is a frequency equal to the pump body natural frequency or a frequency less than 5% different from the pump body natural frequency in the 5 frequencies, judging that resonance exists when the water pump is running, re-making a water pump model selection scheme, and executing step 102; otherwise, step 1063 is performed.
Step 1063, if the frequency N times of the impeller rotation frequency is available in the 5 frequencies, judging that the main source of the hydraulic excitation is dynamic and static interference of the hydraulic component of the water pump, and optimizing the hydraulic component of the water pump in the water pump model selection scheme, wherein the method comprises the steps of adjusting the inlet and outlet setting angles of the impeller blades, adjusting the inlet and outlet setting angles of the guide vane blades, adjusting the distance between the impeller and the guide vane body, adjusting the size of the clearance at the top of the impeller, and adjusting one or more of the number, the wrap angle and the height of the guide vane blades, and executing step 102; otherwise, if the total energy of vibration reaches the minimum value or no change occurs, which indicates that the hydraulic excitation using the dynamic and static interference as the source is effectively suppressed, step 1064 is executed; otherwise, continuing to optimize the main pump hydraulic component in the water pump model selection scheme, and executing step 102. Wherein N is an integer greater than or equal to 1. Impeller frequency conversion，/>Representing the number of leaves,/>The rated rotation speed of the water pump is expressed in r/s.
Step 1064, optimizing an engineering runner in a water pump model selection scheme, including designing an anti-rotation plate in a water inlet runner, adjusting the section transition of the water inlet runner, adjusting the back wall distance of a pump body shaft, adjusting the section transition of a water suction horn, adjusting the diffusion angle of a guide vane body and adjusting the center radius of a water outlet elbow, and executing step 102; if the total vibration energy reaches the minimum value or no change occurs any more, the hydraulic excitation taking other bad flow states as main sources is effectively inhibited, and then the optimal vibration reduction scheme of the impeller in the x direction is obtained; otherwise, continuing to optimize the engineering runner in the water pump model selection scheme, and executing step 102.
Preferably, the method further comprises:
Step 1065, calculating the vibration damping total energy of the optimal vibration damping scheme of the impeller in the x direction by using the formula (6-1):
(6-1)
In the method, in the process of the invention,Representing the total vibration reduction energy of the optimal vibration reduction scheme of the impeller in the x direction,/>Representing total energy of vibration of impeller in x direction in initial water pump model selection schemeRepresenting the total vibration energy of the optimal vibration damping scheme of the impeller in the x direction.
By adopting the method, the main source of hydraulic excitation is judged according to the component force frequency domain data of the impeller in the y direction, and optimization is carried out aiming at different sources, so that the optimal vibration reduction scheme of the impeller in the y direction is obtained. And judging main sources of hydraulic excitation according to the component force frequency domain data of the guide vane body in the x direction, and optimizing according to different sources to obtain an optimal vibration reduction scheme of the guide vane body in the x direction. Judging main sources of hydraulic excitation according to the component force frequency domain data of the pump body wall surface in the x direction, and optimizing the main sources to obtain an optimal vibration reduction scheme of the pump body wall surface in the x direction. And judging the main source of hydraulic excitation according to the frequency domain data of the resultant force in the x direction, and optimizing the main source according to different sources to obtain the optimal vibration reduction scheme of the resultant force in the x direction.
Meanwhile, the total vibration energy of the impeller in the y direction, the total vibration energy of the guide vane body in the x direction, the total vibration energy of the guide vane body in the y direction, the total vibration energy of the pump body wall surface in the x direction, the total vibration energy of the pump body wall surface in the y direction, the total vibration energy of the resultant force in the x direction and the total vibration energy of the resultant force in the y direction are also obtained.
The method of the embodiment of the invention selects the water pump hydraulic component which directly acts on the fluid as a vibration analysis object on the basis of establishing a calculation model and a fluid control equation, and comprises the key areas of an impeller, a guide vane body, a water pump body wall surface and the like, radial force component functions of the water pump hydraulic component and water pump radial resultant force functions are written, pump body radial force data are obtained in the calculation process, frequency domain conversion is carried out on the radial force time domain data based on the FFT principle, the main source of hydraulic excitation is judged according to main frequency components, optimization is carried out on different vibrations, the optimization effect is evaluated by adopting the total energy of the vibration, resonance is eliminated, the optimal water pump model is obtained, and the damping effect of the optimal water pump model is evaluated by adopting the damping total energy index. The research object of the traditional pressure pulsation algorithm is a plurality of infinitely small monitoring points in fluid, and the vibration condition is indirectly reflected according to the pulse characteristics of the fluid points. The radial force data obtained by the method can more directly and accurately reflect the vibration amplitude and frequency of different parts, so that the vibration source components can be accurately judged and the direction can be clearly optimized. Compared with a method for realizing vibration reduction by researching a vibration mechanism through a vibration experiment, the method can save a great deal of time cost and economic cost, and directly avoid the problem that an experimental model device is inconsistent with an engineering model. Moreover, the method has extremely strong universality, and can be suitable for various different types of water pump system engineering because the modeling optimization is carried out on the water pump system engineering. The hydraulic excitation characteristics which can be respectively generated by using different types of water pumps in one project can be obtained by adopting the method.
According to the method, the impeller is considered to be a rotating part in the running process of the water pump, the guide vane body and the wall surface of the whole pump body are considered to be static parts, when the main source of hydraulic excitation is judged according to the main frequency component and the optimization is carried out on different vibrations, the impeller, the guide vane body and the wall surface of the pump body are respectively judged and optimized, and the dynamic and static parts can be subjected to independent vibration analysis, so that the information of the working states of the parts can be obtained, the aim of clear optimization is facilitated, and the optimization efficiency is improved. And the total force is judged and optimized, and the overall vibration condition of the engineering can be evaluated to know the overall effect of vibration reduction optimization.
A specific example is provided below, and the method of the invention is used for optimizing the hydraulic excitation problem of the rainwater pump station.
Step1, an initial water pump model selection scheme is formulated according to engineering requirements of a rainwater pump station.
And 2, carrying out three-dimensional modeling on the water pump and the engineering environment in the water pump model selection scheme by adopting UG three-dimensional modeling software to obtain a calculation model, as shown in figure 2. And performing grid division on the established calculation model, and performing encryption grid treatment on key areas such as a near wall surface, impellers, guide vane bodies and the like or engineering local fine positions to obtain a discrete model.
And 3, performing steady calculation on the discrete model by adopting CFD computational fluid dynamics software. Before calculation, the impeller area is set as a rotation area, and the rotating speed is set according to the rated rotating speed 490 r/min. The water pump is in an axial flow type, and the dynamic and static areas are connected through a stage interface. The total step size of steady state calculation is initially set to 3000 steps, and the convergence standard of the steady state is that the RMS value of the residual curve is lower than 1.0E-4. A fluid control equation is established. And obtaining a static calculation result after calculation.
And step 4, setting the calculation type as implicit unsteady calculation initial conditions by taking the result file of the unsteady calculation in the step 3. The time step of the unsteady calculation is set as the time of 3 DEG rotation of the impeller, the total calculated time length is the time of 6 revolutions of the impeller, and the minimum iteration number of each time step is set as 10. Before calculation starts, the radial component force function of the water pump hydraulic component shown in the formulas (1) to (4) and the radial resultant force function of the water pump shown in the formula (5) are written in computational fluid dynamics software, data are set for the written functions, and the storage frequency is stored once every 1 time step. Since the result of the unsteady calculated value is more stable in the later period, the calculation result of the last 3 circles is taken for preservation and analysis. As shown in fig. 3, the curves in the figure are composed of radial force data fix and fiy of the last 3 circles of impellers in the x and y directions respectively, and it can be seen that the fix and fiy time domain data show obvious periodic fluctuation.
And step 5, performing frequency domain conversion on the water pump radial force time domain data of the last 3 circles according to the FFT conversion principle to obtain water pump radial force frequency domain data, as shown in fig. 4.
And 6, judging a main source of hydraulic excitation according to the component force frequency domain data of the impeller in the x direction, and optimizing aiming at different sources to obtain an optimal vibration reduction scheme of the impeller in the x direction. And judging main sources of hydraulic excitation according to the component force frequency domain data of the impeller in the y direction, and optimizing according to different sources to obtain an optimal vibration reduction scheme of the impeller in the y direction. And judging main sources of hydraulic excitation according to the component force frequency domain data of the guide vane body in the x direction, and optimizing according to different sources to obtain an optimal vibration reduction scheme of the guide vane body in the x direction. Judging main sources of hydraulic excitation according to the component force frequency domain data of the pump body wall surface in the x direction, and optimizing the main sources to obtain an optimal vibration reduction scheme of the pump body wall surface in the x direction. And judging the main source of hydraulic excitation according to the frequency domain data of the resultant force in the x direction, and optimizing the main source according to different sources to obtain the optimal vibration reduction scheme of the resultant force in the x direction.
In the distinguishing process, impeller rotation frequency and frequency multiplication of impeller rotation frequency exist, so that dynamic and static interference factors of hydraulic components are judged to exist as a source of hydraulic excitation, an adopted optimization scheme is to keep a guide vane body of an original water pump unit, replace an impeller model with the same specific rotation speed, and adjust an inlet and outlet angle and a placement angle of an impeller to be matched with the original guide vane body. In addition, other components except the impeller frequency conversion exist, the main vibration source component is described to further comprise poor flow states in a pump station flow channel, in order to eliminate the poor flow states, an adopted optimization scheme is to shorten a transmission shaft of an axial flow pump, so that the impeller, an impeller chamber, a guide vane body and a water suction horn are integrally upwards, the scheme effectively improves the speed gradient distribution in the water suction horn, and good inflow conditions are provided for the water pump impeller.
And 7, after optimization, the total vibration energy of the impeller in the x direction is reduced from 6061.43 of the original scheme to 43.44 after optimization, and the total vibration reduction energy reaches 21.45db. The total vibration energy of the impeller in the y direction is reduced to 11.87 from 3126.71 in the original scheme, and the total vibration reduction energy reaches 24.21db. The vibration energy of each component of other components is reduced by more than 10db, and the total vibration reduction energy of the resultant force is maximally more than 50 db.
The foregoing has shown and described the basic principles, principal features and advantages of the invention. It will be understood by those skilled in the art that the present invention is not limited to the specific embodiments described above, and that the above specific embodiments and descriptions are provided for further illustration of the principles of the present invention, and that various changes and modifications may be made therein without departing from the spirit and scope of the invention as defined in the appended claims. The scope of the invention is defined by the claims and their equivalents.
Claims (10)
1. A hydraulic excitation optimization control method based on pump radial force distribution is characterized by comprising the following steps:
Step 101, an initial water pump model selection scheme is formulated according to actual engineering requirements;
102, carrying out three-dimensional modeling on a water pump and an engineering environment in a water pump model selection scheme, and carrying out grid division on an established calculation model to obtain a discrete model;
Step 103, performing steady calculation on the discrete model by using computational fluid dynamics software to obtain a static calculation result;
104, based on a static calculation result, performing unsteady calculation on the discrete model by using computational fluid dynamics software; in the calculation process, calculating to obtain water pump radial force time domain data through a water pump radial force function;
step 105, performing frequency domain conversion on the water pump radial force time domain data to obtain water pump radial force frequency domain data;
and 106, judging main sources of hydraulic excitation according to the radial force frequency domain data of the water pump, and optimizing aiming at different sources to obtain an optimal vibration reduction scheme.
2. The hydraulic excitation optimization control method based on pump radial force distribution according to claim 1, wherein the water pump radial force time domain data comprises radial component force time domain data of an impeller, radial component force time domain data of a guide vane body, radial component force time domain data of a pump wall surface and water pump radial resultant force time domain data;
In the step 104, before the unsteady calculation is performed, a radial component force function of the hydraulic component of the water pump and a radial resultant force function of the water pump are written in computational fluid dynamics software.
3. The hydraulic excitation optimization control method based on pump radial force distribution according to claim 2, wherein the radial component force function of the hydraulic component of the water pump comprises a radial component force function of an impeller shown in formula (1), a radial component force function of a guide vane body shown in formula (2), and a radial component force function of a pump wall surface shown in formula (3):
(1)
(2)
(3)
The radial resultant force function of the water pump is shown as (4):
(4)
In the method, in the process of the invention,Representing the radial component of the impeller,/>Representing the radial component of the vane body,/>Representing the radial component of the pump body wall surface,/>Representing the radial resultant force of the water pump,/>Representing self-contained radial force functions in computational fluid dynamics software,/>Representing the name of the impeller in the computational model,/>Representing the name of the vane body in the computational model,/>The name of the pump body wall in the calculation model is indicated.
4. The hydraulic excitation optimization control method based on pump radial force distribution according to claim 2, wherein in step 106, main sources of hydraulic excitation are determined according to radial component force frequency domain data and radial resultant force frequency domain data of each water pump hydraulic component, and optimization is performed for different sources to obtain an optimal vibration reduction scheme of component force of each water pump hydraulic component and an optimal vibration reduction scheme of resultant force of the water pump.
5. The hydraulic excitation optimization control method based on pump radial force distribution according to claim 1, wherein the step 106 specifically includes:
step 1061, sorting the radial force frequency domain data of the water pump according to the magnitude from large to small to obtain the magnitude of the top 5 bits 、/>、/>、/>And/>5 Frequencies/>, respectively corresponding、/>、/>、/>And/>；
The total energy of vibration is calculated using equation (5):
(5)
Step 1062, if there is a frequency equal to the pump body natural frequency or a frequency less than 5% of the pump body natural frequency difference in the 5 frequencies, re-making a pump model selection scheme, and executing step 102; otherwise, go to step 1063;
Step 1063, if there is a frequency N times greater than the impeller rotation frequency in the 5 frequencies, where N is an integer greater than or equal to 1, optimizing a hydraulic component of the pump in the pump model selection scheme, and executing step 102; otherwise, if the total energy of vibration reaches a minimum or no more change occurs, then step 1064 is performed; otherwise, optimizing the hydraulic component of the main pump in the water pump model selection scheme, and executing step 102;
step 1064, optimizing an engineering runner in the water pump model selection scheme, and executing step 102; if the total vibration energy reaches the minimum value or no change occurs any more, an optimal vibration reduction scheme is obtained; otherwise, the engineering runner in the water pump model selection scheme is optimized, and step 102 is executed.
6. The method of optimizing control of hydraulic excitation based on pump radial force distribution according to claim 5, wherein the step 106 further comprises:
Step 1065, calculating the vibration damping total energy of the optimal vibration damping scheme by using the formula (6):
(6)
In the method, in the process of the invention,Represents the total vibration reduction energy of the optimal vibration reduction scheme,/>Representing the total energy of vibration of the initial water pump option,Representing the total vibration energy of the optimal damping scheme.
7. The method of optimizing control of hydraulic excitation based on radial force distribution of a pump body according to claim 5, wherein the method of optimizing hydraulic components of the pump in the pump model selection scheme comprises one or more of adjusting inlet and outlet mounting angles of impeller blades, adjusting inlet and outlet mounting angles of guide vane blades, adjusting a distance between the impeller and the guide vane body, adjusting a blade tip gap size, and adjusting the number, wrap angle and height of the guide vane blades.
8. The method of optimizing control of hydraulic excitation based on radial force distribution of a pump body according to claim 5, wherein the method of optimizing the engineering flow passage in the water pump model selection scheme comprises one or more of designing a rotation preventing plate in the water inlet flow passage, adjusting a section transition of the water inlet flow passage, adjusting a rear wall distance of a pump body shaft, adjusting a section transition of a water suction horn, adjusting a vane diffusion angle and adjusting a center radius of a water outlet elbow.
9. The hydraulic excitation optimization control method based on pump radial force distribution according to claim 1, wherein in step 105, frequency domain conversion is performed on the water pump radial force time domain data of the last 3 circles in the calculation process.
10. The hydraulic excitation optimization control method based on pump radial force distribution according to claim 1, wherein in the step 102, grid encryption processing is performed on the hydraulic component area of the water pump when grid division is performed.
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Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080031741A1 (en) * | 2006-08-02 | 2008-02-07 | Torres Martin R | Jet pump slip joint with axial grooves |
| CN103077292A (en) * | 2013-01-16 | 2013-05-01 | 江苏大学 | Method for predicting hydraulic noise of centrifugal pump |
| CN103226634A (en) * | 2013-04-19 | 2013-07-31 | 华南理工大学 | Computing method for unsteady flow field of rotary jet pump based on three-dimensional dynamic mesh |
| CN104298869A (en) * | 2014-10-07 | 2015-01-21 | 北京理工大学 | Method for predicting fluid-solid coupled characteristic value of elastic hydrofoil |
| CN107273570A (en) * | 2017-05-10 | 2017-10-20 | 江苏大学 | A kind of blade pump cavitation Inductive noise Numerical Prediction Method |
| CN107423512A (en) * | 2017-07-28 | 2017-12-01 | 广东省智能制造研究所 | A kind of light-weight design method of large-scale die-casting machine tailgate |
| CN109268200A (en) * | 2018-08-29 | 2019-01-25 | 哈尔滨工业大学 | It is a kind of for pump turbine fly ease transient process dynamic characteristic and inner flowing characteristic analysis method |
| CN110162864A (en) * | 2019-05-15 | 2019-08-23 | 江苏省水利勘测设计研究院有限公司 | Low lift way traffic pumping station system stability prediction method |
| CN110674596A (en) * | 2019-08-01 | 2020-01-10 | 浙江理工大学 | Method for designing rotor part of multistage centrifugal pump with consideration of operating environment and stability |
| CN111209637A (en) * | 2020-01-14 | 2020-05-29 | 江苏大学 | Method for calculating fluid excitation force of centrifugal pump impeller under eccentric vortex |
| CN111400941A (en) * | 2019-01-03 | 2020-07-10 | 江苏大学 | Numerical prediction method for internal reflux and reflux vortex cavitation of vane pump |
| WO2021129408A1 (en) * | 2019-12-25 | 2021-07-01 | 江苏大学 | Design method for outer contour structure of tire for reducing tire wind resistance |
| CN113947043A (en) * | 2021-10-14 | 2022-01-18 | 华能(浙江)能源开发有限公司清洁能源分公司 | Method and system for monitoring vibration frequency of submarine pipeline based on CFD simulation |
| WO2022011726A1 (en) * | 2020-07-17 | 2022-01-20 | 天华化工机械及自动化研究设计院有限公司 | Ansys-based heat exchanger tube bundle modal analysis method in liquid filling state |
| CN115577493A (en) * | 2022-08-31 | 2023-01-06 | 浙江大学 | Method for predicting unsteady characteristics of blades of horizontal-axis tidal current energy water turbine |
-
2024
- 2024-04-09 CN CN202410419313.4A patent/CN118013894B/en active Active
Patent Citations (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080031741A1 (en) * | 2006-08-02 | 2008-02-07 | Torres Martin R | Jet pump slip joint with axial grooves |
| CN103077292A (en) * | 2013-01-16 | 2013-05-01 | 江苏大学 | Method for predicting hydraulic noise of centrifugal pump |
| CN103226634A (en) * | 2013-04-19 | 2013-07-31 | 华南理工大学 | Computing method for unsteady flow field of rotary jet pump based on three-dimensional dynamic mesh |
| CN104298869A (en) * | 2014-10-07 | 2015-01-21 | 北京理工大学 | Method for predicting fluid-solid coupled characteristic value of elastic hydrofoil |
| CN107273570A (en) * | 2017-05-10 | 2017-10-20 | 江苏大学 | A kind of blade pump cavitation Inductive noise Numerical Prediction Method |
| CN107423512A (en) * | 2017-07-28 | 2017-12-01 | 广东省智能制造研究所 | A kind of light-weight design method of large-scale die-casting machine tailgate |
| CN109268200A (en) * | 2018-08-29 | 2019-01-25 | 哈尔滨工业大学 | It is a kind of for pump turbine fly ease transient process dynamic characteristic and inner flowing characteristic analysis method |
| CN111400941A (en) * | 2019-01-03 | 2020-07-10 | 江苏大学 | Numerical prediction method for internal reflux and reflux vortex cavitation of vane pump |
| CN110162864A (en) * | 2019-05-15 | 2019-08-23 | 江苏省水利勘测设计研究院有限公司 | Low lift way traffic pumping station system stability prediction method |
| CN110674596A (en) * | 2019-08-01 | 2020-01-10 | 浙江理工大学 | Method for designing rotor part of multistage centrifugal pump with consideration of operating environment and stability |
| WO2021129408A1 (en) * | 2019-12-25 | 2021-07-01 | 江苏大学 | Design method for outer contour structure of tire for reducing tire wind resistance |
| CN111209637A (en) * | 2020-01-14 | 2020-05-29 | 江苏大学 | Method for calculating fluid excitation force of centrifugal pump impeller under eccentric vortex |
| WO2022011726A1 (en) * | 2020-07-17 | 2022-01-20 | 天华化工机械及自动化研究设计院有限公司 | Ansys-based heat exchanger tube bundle modal analysis method in liquid filling state |
| CN113947043A (en) * | 2021-10-14 | 2022-01-18 | 华能(浙江)能源开发有限公司清洁能源分公司 | Method and system for monitoring vibration frequency of submarine pipeline based on CFD simulation |
| CN115577493A (en) * | 2022-08-31 | 2023-01-06 | 浙江大学 | Method for predicting unsteady characteristics of blades of horizontal-axis tidal current energy water turbine |
Non-Patent Citations (5)
| Title |
|---|
| CHALGHOUM: "The effects of the rotor-stator interaction on unsteady pressure pulsation and radial force in a centrifugal pump", 《JOURNAL OF HYDRODYNAMICS》, 31 December 2018 (2018-12-31), pages 672 - 681 * |
| YAN P: "Computational fluid dynamics-based pump redesign to improve efficiency and decrease unsteady radial forces", 《JOURNAL OF FLUIDS ENGINEERING》, 31 December 2017 (2017-12-31), pages 139 * |
| 中国动力工程学会: "《火力发电设备技术手册》", 31 December 1996, 机械工业出版社, pages: 433 - 445 * |
| 寇家庆: "非定常气动力建模与流场降阶方法研究", 《中国优秀硕士学位论文全文数据库基础科学辑》, 15 June 2020 (2020-06-15), pages 004 - 34 * |
| 施卫东;张磊;陈斌;蒋婷;张华;: "离心泵间隙对压力脉动及径向力的影响", 排灌机械工程学报, no. 03, 30 May 2012 (2012-05-30), pages 1 * |
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