CN116522516A - Method for modeling hydraulic turbine pump element based on Flowmaster - Google Patents
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Abstract
The application provides a method for modeling a hydraulic turbine pump element based on a Flowmaster, which comprises the following steps: a simplified hydraulic turbine pump model is built, the simplified model comprises a power fuel branch representing a turbine channel and an oil supply branch representing an impeller channel, and a linear equation of mass flow and pressure of the turbine channel and the impeller channel is built according to a general linear equation of multiple interface elements; obtaining a mapping relation between pressure difference and volume flow according to performance curves and performance curved surfaces of a turbine channel and an impeller channel of the hydraulic turbine pump, further obtaining a linear equation of the hydraulic turbine pump, and establishing the linear equation of the turbine channel and the impeller channel in a normal working state mode; in an abnormal working state mode, the hydraulic turbine pump is regarded as a resistance element, and a linear equation of a turbine channel and an impeller channel in the abnormal working state mode is established; and performing steady-state test and transient test of the hydraulic turbine pump element, and verifying the correctness of the turbine channel and the impeller channel of the hydraulic turbine pump element.
Description
Technical Field
The application belongs to the technical field of design of an aircraft fuel system pipe network, and particularly relates to a method for modeling a hydraulic turbine pump element based on a Flowmaster.
Background
In the engineering of aircraft fuel systems, it is necessary to supply fuel distributed in the individual tanks to the consumer compartment and to supply the engine with fuel from the consumer compartment. Depending on functional requirements, fuel pumps are often required to deliver and boost fuel. A hydro turbine pump is a fuel pump driven by a hydro turbine. The dynamic fuel oil flows into the oil injection device of the hydraulic turbine pump under the pressure effect, the kinetic energy of liquid flow is increased by changing the flow cross-sectional area, and the dynamic fuel oil enters into the blades of the axial flow turbine through the oil injection opening of the oil injection device to impact the blades, so that the turbine rotates to generate mechanical energy, thereby driving the impeller rigidly connected with the turbine to rotate, and realizing the function of the pump.
In the process of simulating and calculating the pipe network performance of the fuel system by using the fluid design software FlowMaster, the inlet and outlet flow and the pressure drop of the hydraulic turbine pump are key parameters. However, the FlowMaster existing component library lacks the component simulation model and cannot meet engineering design requirements. Therefore, to ensure the accuracy of the simulation calculation, a Flowmaster bypass valve component and a bypass valve simulation model need to be established to meet the requirements of the fuel system simulation calculation.
Disclosure of Invention
It is an object of the present application to provide a method of modeling a hydraulic turbine pump element based on Flowmaster to solve or mitigate at least one problem in the background art.
The technical scheme of the application is as follows: a method of Flowmaster-based modeling of a hydraulic turbine pump element, the method comprising:
a simplified hydraulic turbine pump model is built, the simplified model comprises a power fuel branch representing a turbine channel and an oil supply branch representing an impeller channel, and a linear equation of mass flow and pressure of the turbine channel and the impeller channel is built according to a general linear equation of multiple interface elements;
obtaining a mapping relation between pressure difference and volume flow according to performance curves and performance curved surfaces of a turbine channel and an impeller channel of the hydraulic turbine pump, and obtaining a linear equation of the hydraulic turbine pump according to the mapping relation and combining known conditions, so as to determine coefficients of linear equations of a power fuel branch and an oil supply branch, and establish the linear equations of the turbine channel and the impeller channel in a normal working state mode;
in an abnormal working state mode, the hydraulic turbine pump is regarded as a resistance element; when the flow resistance characteristic curves of the turbine channel and the impeller channel are adopted, the coefficients of the linear equations of the power fuel branch and the fuel supply branch are determined according to the mapping relation between the pressure difference and the volume flow, and the linear equations of the turbine channel and the impeller channel under an abnormal working state mode are established; when the flow resistance coefficients of the turbine channel and the impeller channel are adopted, the coefficients of the linear equations of the power fuel branch and the fuel supply branch are determined according to the flow equation and the mass conservation law, and the linear equations of the turbine channel and the impeller channel under an abnormal working state mode are established;
and performing steady-state test and transient test of the hydraulic turbine pump element, and verifying the correctness of the turbine channel and the impeller channel of the hydraulic turbine pump element.
Further, the general format of the multi-interface element is:
further, the linear equation of the turbine channel is:
the linear equation of the impeller channel is:
further, the turbine passage linear equation under the normal working state of the hydraulic turbine pump is as follows:
the coefficients of the turbine channel linear equation are:
further, the impeller channel linear equation under the normal working state of the hydraulic turbine pump is as follows:
the coefficients of the impeller channel linear equation are respectively:
further, when the flow resistance characteristic curve is adopted, the modeling method of the linear equation of the turbine channel and the impeller channel in the abnormal working state mode is the same as the modeling method of the hydraulic turbine pump in the normal working state.
Further, the turbine passage linear equation under the abnormal working state of the hydraulic turbine pump is as follows:
the coefficients of the turbine channel linear equation are:
further, the impeller channel linear equation under abnormal working condition of the hydraulic turbine pump is as follows:
the coefficients of the impeller channel linear equation are respectively:
the method provided by the application can realize effective calculation of inlet and outlet fuel pressure and flow of the hydraulic turbine pump model in the FlowMaster software, enrich the FlowMaster software component library, supplement the simulation model of the fuel system accessories, and effectively support engineering design requirements of FlowMaster on system pipe network and performance simulation calculation thereof.
Drawings
In order to more clearly illustrate the technical solutions provided by the present application, the following description will briefly refer to the accompanying drawings. It will be apparent that the figures described below are only some embodiments of the present application.
FIG. 1 is a flow chart of a modeling method of the present application.
FIG. 2 is a schematic diagram of the hydraulic turbine pump architecture of the present application;
FIG. 3 is a simplified schematic diagram of a hydraulic turbine pump of the present application;
FIGS. 4a and 4b are schematic diagrams of turbine channel performance curves and impeller channel performance curves of a hydro turbine pump according to an embodiment of the present application;
FIGS. 5 a-5 c are schematic diagrams of parameter settings of a hydraulic turbine pump unit in FlowMaster software, respectively, according to an embodiment of the present application;
FIGS. 6a and 6b are schematic diagrams of steady state and transient test piping networks, respectively, of a hydraulic turbine pump element in a Flowmaster according to an embodiment of the present application;
FIG. 7 is a schematic view of a variation curve of the flow rate at the outlet of the impeller channel according to an embodiment of the present application;
fig. 8 is a schematic diagram of a pressurized transient test pipe network of a hydro turbine pump element in a Flowmaster according to an embodiment of the application.
Detailed Description
In order to make the purposes, technical solutions and advantages of the implementation of the present application more clear, the technical solutions in the embodiments of the present application will be described in more detail below with reference to the accompanying drawings in the embodiments of the present application.
As shown in fig. 1, the method for modeling a hydraulic turbine pump element based on a Flowmaster provided by the application comprises the following steps:
step one: and establishing a hydraulic turbine pump linear equation.
The hydraulic turbine pump model is simplified, the simplified model is divided into two branches, one is a power fuel branch and is used for impacting the turbine to generate mechanical energy, and the parameters of inlet and outlet nodes are respectively Q 1 、P 1 、Q 2 、P 2 The method comprises the steps of carrying out a first treatment on the surface of the The other branch is an oil supply branch communicated with the inside of the oil tank, and the parameters of the inlet and outlet nodes are respectively Q 3 、P 3 、Q 4 、P 4 。
And (3) linearizing the flow equation of the fluid element based on the FlowMaster, and solving parameters such as pressure, flow speed and the like of the element by solving a linear equation set.
And establishing a linear equation of the mass flow and the pressure of the power fuel branch and the fuel supply branch according to a general linear equation of the multi-interface element.
As shown in fig. 2, which is a schematic diagram of a hydraulic turbine pump structure in the application, the dynamic fuel flows into the fuel injection device 1 under the action of pressure, the kinetic energy of the fluid flow is increased by changing the flow cross-sectional area, and the kinetic energy enters into the blades 3 of the axial flow turbine 2 through the fuel injection port of the device to impact the blades 3, so that the turbine rotates, mechanical energy is generated, and the impeller 4 rigidly connected with the turbine is driven to rotate, thereby realizing the function of the turbine pump.
FIG. 3 is a simplified schematic diagram of a hydraulic turbine pump according to the present application, wherein the simplified model is divided into two branches, one is a power fuel branch (i.e. turbine passage) for impacting the turbine to generate mechanical energy, and the inlet and outlet node parameters are respectively Q 1 、P 1 、Q 2 、P 2 The method comprises the steps of carrying out a first treatment on the surface of the The other branch is an oil supply branch (namely an impeller passage) communicated with the inside of the oil tank, and the inlet and outlet node parameters are respectively Q 3 、P 3 、Q 4 、P 4 。
According to the linear equation construction rule of the multi-interface element, element node linear equations of any n interfaces can be obtained, and the equations can be written as the following formulas:
no.1 interface:
no.2 interface:
……
no. n interface:
thereby obtaining the general format thereof
The linear equation that can then be deduced for the turbine channels and impeller channels of the hydro turbine pump is:
turbine passage:
impeller channel:
step two: and establishing a turbine channel and impeller channel linear equation under the normal working state mode of the hydraulic turbine pump.
And obtaining the mapping relation between the pressure difference and the volume flow according to the performance curves and the performance curved surfaces of the turbine channels and the impeller channels of the hydraulic turbine pump. The linear equation of the hydraulic turbine pump is obtained through transformation by combining the mapping relation with the known condition, so that the coefficients of the linear equation of the power fuel branch and the oil supply branch can be determined, and the linear equation of the turbine channel and the impeller channel in the normal working state mode is established.
The performance curve of the turbine channel of the hydro turbine pump is shown in fig. 4a, and the performance curve of the impeller channel is shown in fig. 4b, wherein the performance curve/curve establishes the relationship between the pressure difference and the flow of the turbine channel and the impeller channel. The performance curve/curved surface can show that a certain mapping relation exists between the pressure difference and the flow, namely:
turbine channel performance curve: ΔP 1 ＝P 1 -P 2 ＝f(Q t ) (3)
Impeller channel performance curve: ΔP 2 ＝P 4 -P 3 ＝g(Q t ,Q p )。 (4)
2.1 Establishment of turbine passage linear equation
From the initial boundary conditions, carry-over 3 is available (Q [0] ，ΔP [0] ) And (3) taking n points in a specified area near the point to perform polynomial fitting to obtain a polynomial:
the method comprises the following steps of:
from flow relationshipSubstituting the above formula to obtain:
according to the principle of "inflow is negative and outflow is positive", the linear equation of the turbine channel is known as:
comparing the above equation with the general linear equation 1, the coefficients of the linear equation can be obtained as follows:
thereby creating a turbine passage linear equation.
2.2 Impeller channel linear equation establishment
As can be seen from the curved performance surface of the impeller channel in fig. 4b, the characteristic curve of the impeller channel is a flow differential pressure curve set under different flow rates of the impeller channel, and the nature of the curve is still a problem for solving the curve. Similar to the method for isomorphism construction of the turbine channel linear equation, the flow Q of the impeller channel t Taking n points down to perform polynomial fitting to obtain a polynomial
Through transformation to obtain
From flow relationshipSubstituting the above formula to obtain:
i.e.
According to the principle of "inflow is negative and outflow is positive", the linear equation of the turbine channel is known as:
comparing the above and general linear equation (2), the coefficients of the obtained linear equations are respectively
Step three: and establishing a turbine channel and impeller channel linear equation under the abnormal working state mode of the hydraulic turbine pump.
In the abnormal operating state mode, the hydro turbine pump is considered as a resistance element. When the flow resistance characteristic curves of the turbine channel and the impeller channel are adopted, the coefficients of the linear equations of the power fuel branch and the fuel supply branch can be determined by transformation according to the mapping relation between the pressure difference and the volume flow and combining known conditions, and the linear equations of the turbine channel and the impeller channel under an abnormal working state mode are established. When the flow resistance coefficients of the turbine channel and the impeller channel are adopted, the coefficients of the linear equations of the power fuel branch and the fuel supply branch can be determined through transformation according to the flow equation and the mass conservation law, and the linear equations of the turbine channel and the impeller channel under the abnormal working state mode are established.
The specific process is as follows: when the actual flow Q of the turbine channel of the hydraulic turbine pump 1 ＜Q 1min When the hydraulic turbine pump is in abnormal working state, the turbine pump is treated by the resistance element, and the flow resistance coefficient of the turbine channel and the impeller channel (the flow resistance coefficient k of the turbine channel) t Flow resistance coefficient k of impeller channel p ) Or a flow resistance characteristic curve (turbine channel flow resistance characteristic curve DeltaP) 1 ＝P 1 -P 2 ＝f(Q 1 ) Flow resistance characteristic curve delta P of impeller channel 2 ＝P 3 -P 4 ＝f(Q 2 ) A) modeling.
When the flow resistance characteristic curve is adopted, the modeling mode is the same as that of the turbine pump in the normal working state.
When a given flow resistance coefficient is used, the flow equation is followed:
is obtained by conservation of mass
Solving the two problems simultaneously to obtain
Is prepared through finishing
Wherein: a is that t 、A p Is the flow resistance coefficient k t 、k p Corresponding to the cross-sectional area at the flow rate. I.e. when the flow resistance coefficient k t 、k p Relative to the inlet flow rate, then there is A t ＝A 1 、A p ＝A 3 The method comprises the steps of carrying out a first treatment on the surface of the When the flow resistance coefficient k t 、k p At a relative outlet flow rate, then there is A t ＝A 2 、A p ＝A 4 。
The corresponding linear equation and coefficients are thus obtained as:
turbine passage
Impeller channel
Step four: and testing a hydraulic turbine pump element.
Performing steady-state test on the hydraulic turbine pump element, and testing the accuracy of pressure drop calculation of a turbine channel by setting the flow of the turbine channel; and by setting a certain turbine flow, testing the accuracy of the calculation of the impeller pressure rise corresponding to different impeller flows.
And carrying out transient test on the element of the hydraulic turbine pump, and respectively carrying out correctness test on the pressure rise of the turbine pump when the outlet flow of the impeller channel is a fixed value and the flow is changed under the condition that the inlet pressure and the outlet flow of the turbine channel are fixed.
And performing a hydraulic turbine pump element compressible transient test, verifying that the hydraulic turbine pump element can be connected with the compressible element for use, and correctly calculating the compressible transient.
The list of parameters entered for the hydro turbine pump element in the Flowmaster software is shown in fig. 5a, wherein the equivalent diameter of the turbine and impeller inlet and outlet, the minimum working flow rate of the turbine channel, and the loss coefficients of the turbine channel and impeller channel are the necessary parameters entered, the schematic diagram of the hydro turbine pump element parameter set is shown in fig. 5b, and the loss element parameter set is shown in fig. 5 c. Table 1 is the hydro turbine pump element output parameters.
TABLE 1 output parameters of hydraulic turbine pump elements
As shown in fig. 6a, a steady-state test pipe network of a hydro turbine pump element is shown, steady-state test is performed on the developed hydro turbine pump element through the test pipe network, and accuracy of interpolation calculation of a preset turbine channel characteristic curve and an impeller channel characteristic curve of the hydro turbine pump element is verified, including:
1) Testing the accuracy of the pressure drop calculation of the turbine channel by setting the flow of the turbine channel;
2) And by setting a certain turbine flow, testing the accuracy of the calculation of the impeller pressure rise corresponding to different impeller flows.
In steady state testing, the turbine channel inlet pressure was 5.5bar and the impeller channel inlet pressure was 1bar. The turbine channel flow adopted in the turbine channel pressure drop test is respectively as follows: 0.00086m3/s,0.00139m3/s,0.00204m3/s,0.0024m3/s,0.00278m3/s.
Impeller channel pressure variation test the flow boundaries set forth in table 2 below.
Table 2 steady state test impeller channel flow boundary conditions
Turbine passage pressure drop calculation accuracy test results are shown in Table 3 below, except turbine passage flow is 0.00278m 3 And (3) the calculated results of the turbine pumps under other working conditions are matched with the interpolation result outside/s. As can be seen from the turbine passage flow-pressure drop performance curve of FIG. 4 (a), the maximum flow rate of the turbine passage under normal operation is 0.002777m 3 /s, flow 0.00278m 3 And/is beyond the normal operation flow range, so that a certain error exists between the calculation result and the interpolation result.
TABLE 3 turbine passage flow-differential pressure test results
Turbine channel flow rates are set to be 0.00086m respectively 3 /s、0.00204m 3 /s、0.00287m 3 At/s, the results of the calculation correctness test of the impeller pressure rise corresponding to the different impeller flow are shown in the following tables 4-6.
TABLE 4 test and validation results for turbine passage flow of 0.00086m3/s
TABLE 5 test and validation results for turbine channel flow of 0.00204m3/s
TABLE 6 test and validation results for turbine channel flow of 0.00278m3/s
As can be seen from the comparison of the test result and the curve interpolation result, the test result is identical with the curve interpolation result, and the hydraulic turbine pump element has normal use function.
Fig. 6b shows a transient test pipe network of the hydraulic turbine pump element, and the accuracy test is performed on the turbine pump when the turbine channel inlet pressure and the turbine channel outlet flow are constant (constant boundary conditions, table 7 below) and the turbine pump pressure rise (change boundary conditions) when the flow changes. The impeller passage outlet flow rate profile is shown in fig. 7.
TABLE 7 turbine passage inlet pressure and outlet flow
| Element number | Inlet pressure | Turbine outlet flow | Impeller outlet flow |
| Parameter value | 5.5bar | -0.00204m 3 /s | -0.0139m 3 /s |
The constant boundary condition test results are shown in table 8, and the variable boundary condition test results are shown in table 9. As can be seen from the comparison result of the test result and the curve interpolation, the hydraulic turbine pump has normal operation function in the normal working state and meets the development requirement.
TABLE 8 constant boundary condition test results
TABLE 9 constant boundary condition test results
Fig. 8 shows a test network of the hydraulic turbine pump unit in the Flowmaster, which is used to verify that the hydraulic turbine pump unit can be used in connection with the hydraulic unit and to perform the calculation of the hydraulic transient correctly.
The test method is the same as the variable flow boundary condition in the transient test, the pressure boundary of the turbine channel inlet of the hydraulic turbine pump is set to be 14bar, the outlet flow is-0.00204 m < 3 >/s, and the parameter setting of the loss element and the change curve of the flow of the outlet of the impeller channel are unchanged.
The results of the compressible transient test are shown in the following table 10, and the error analysis in table 10 shows that the compressible transient analysis results conform to the curve interpolation results, and the hydraulic turbine pump has correct working performance.
Table 10 compressible transient test results
The method provided by the application can realize effective calculation of inlet and outlet fuel pressure and flow of the hydraulic turbine pump model in the FlowMaster software, enrich the FlowMaster software component library, supplement the simulation model of the fuel system accessories, and effectively support engineering design requirements of FlowMaster on system pipe network and performance simulation calculation thereof.
The foregoing is merely specific embodiments of the present application, but the scope of the present application is not limited thereto, and any changes or substitutions easily conceivable by those skilled in the art within the technical scope of the present application should be covered in the scope of the present application. Therefore, the protection scope of the present application shall be subject to the protection scope of the claims.
Claims (8)
1. A method of Flowmaster-based modeling of a hydraulic turbine pump unit, the method comprising:
a simplified hydraulic turbine pump model is built, the simplified model comprises a power fuel branch representing a turbine channel and an oil supply branch representing an impeller channel, and a linear equation of mass flow and pressure of the turbine channel and the impeller channel is built according to a general linear equation of multiple interface elements;
obtaining a mapping relation between pressure difference and volume flow according to performance curves and performance curved surfaces of a turbine channel and an impeller channel of the hydraulic turbine pump, and obtaining a linear equation of the hydraulic turbine pump according to the mapping relation and combining known conditions, so as to determine coefficients of linear equations of a power fuel branch and an oil supply branch, and establish the linear equations of the turbine channel and the impeller channel in a normal working state mode;
in an abnormal working state mode, the hydraulic turbine pump is regarded as a resistance element; when the flow resistance characteristic curves of the turbine channel and the impeller channel are adopted, the coefficients of the linear equations of the power fuel branch and the fuel supply branch are determined according to the mapping relation between the pressure difference and the volume flow, and the linear equations of the turbine channel and the impeller channel under an abnormal working state mode are established; when the flow resistance coefficients of the turbine channel and the impeller channel are adopted, the coefficients of the linear equations of the power fuel branch and the fuel supply branch are determined according to the flow equation and the mass conservation law, and the linear equations of the turbine channel and the impeller channel under an abnormal working state mode are established;
and performing steady-state test and transient test of the hydraulic turbine pump element, and verifying the correctness of the turbine channel and the impeller channel of the hydraulic turbine pump element.
2. The method of Flowmaster-based modeling of a hydraulic turbine pump unit of claim 1, wherein the general linear equation for the multi-interface unit is:
3. the method of Flowmaster-based modeling of a hydro turbine pump element of claim 2, wherein the linear equation for the turbine passage is:
the linear equation of the impeller channel is:
4. a method of modeling a hydro turbine pump element based on Flowmaster as claimed in claim 3 wherein the turbine passage linear equation for normal operation of the hydro turbine pump is:
the coefficients of the turbine channel linear equation are:
5. the method for modeling a hydro turbine pump element based on Flowmaster of claim 4, wherein the impeller passage linear equation under normal operation of the hydro turbine pump is:
the coefficients of the impeller channel linear equation are respectively:
6. the method for modeling a hydro turbine pump element based on Flowmaster as defined in claim 5 wherein when a flow resistance characteristic is used, the linear equation modeling of the turbine passage and the impeller passage in the abnormal operation state mode is the same as the modeling method of the hydro turbine pump in the normal operation state.
7. The method for modeling a hydro turbine pump element based on Flowmaster of claim 5, wherein the turbine passage linear equation under the abnormal operating condition of the hydro turbine pump is:
the coefficients of the turbine channel linear equation are:
8. the method for modeling a hydro turbine pump element based on Flowmaster of claim 5, wherein the impeller passage linear equation under the abnormal operating condition of the hydro turbine pump is:
the coefficients of the impeller channel linear equation are respectively:
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