CN106481446B - Method for calculating the pressure drop across a flow-blocking component - Google Patents
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1445—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being related to the exhaust flow
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1446—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being exhaust temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1448—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an exhaust gas pressure
- F02D41/145—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an exhaust gas pressure with determination means using an estimation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/24—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means
- F02D41/2406—Electrical control of supply of combustible mixture or its constituents characterised by the use of digital means using essentially read only memories
- F02D41/2409—Addressing techniques specially adapted therefor
- F02D41/2416—Interpolation techniques
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1401—Introducing closed-loop corrections characterised by the control or regulation method
- F02D2041/1433—Introducing closed-loop corrections characterised by the control or regulation method using a model or simulation of the system
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D23/00—Controlling engines characterised by their being supercharged
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention relates to a pressure drop (4) for a first flow-blocking module (4) and a second flow-blocking module (5) arranged parallel thereto, for a turbine of a charging device, in particular driven by exhaust gas) Method for determining, the turbine having a variable turbine geometry and a bypass line with a controllable cross section, the method comprising the following steps: -providing a first flow function (f) for the first component (4)) Critical first pressure drop of (c) (() And a second flow function for the second component (5) (() Critical second pressure drop of (c) (() (ii) a -at normalized first and second flow functions (c:)) And critical first and second pressure drops () A pressure drop function is preset on the basis of the pressure drop; -in dependence of said pressure dropThe function determines (S7-S11) the pressure drop by applying an approximation (S7-S11))。
Description
Technical Field
The present invention relates generally to the calculation of state variables in gas conducting systems with flow-blocking components, in particular for internal combustion engines with supercharging devices driven by exhaust gases. The invention further relates to the field of actuating a supercharger regulator of a supercharging device for an internal combustion engine.
Background
In order to regulate the charging pressure in a supercharged internal combustion engine, in particular a diesel engine, a supercharging device, for example a turbocharger, which is driven by exhaust gas is used. The efficiency of the charging device or the proportion of the mechanical power extracted from the exhaust gas enthalpy which is used to drive the compressor can be set by means of the supercharger regulator. The exhaust-gas-driven charging device, which is used in particular for the variable adjustment of the efficiency of the charging device, may have a controllable variable turbine geometry, a controllable wastegate valve or a combination thereof. Different charging topologies are currently used for motor vehicles, which provide, for example, a single-stage charging, a two-stage charging with two turbochargers connected in series, or a two-stage charging with two turbochargers connected in parallel (stepped charging).
The variable adjustment of the charging device can be realized, for example, by a turbine having a variable geometry (VTG regulator, variable turbine geometry). VTG is used to denote all types of turbines, the efficiency of which can be varied by means of a housing geometry that is variable during operation. This can be done, for example, by means of variable guide vanes.
At present, multi-stage supercharging systems are mainly used to improve the dynamic driving behavior of the vehicle. For example, the series connection of two charging devices allows the use of a charging device with a lower output and a charging device with a higher output, wherein the charging device with the lower output accelerates more quickly due to a lower moment of inertia and thus can produce the motor torque more quickly. For higher motor speeds, this charging device is bypassed due to the higher mass flow, so that the charging pressure is formed only with a charging device having a higher output. In this case, it is currently the case with VTG turbines that the turbine bypass is opened in a regulated manner only when the turbine is no longer able to be regulated by the VTG due to the higher mass flow.
The current regulation strategy takes advantage of all of the boosting topologies described above. A new development describes a single-stage supercharging device having a VTG turbine which additionally has a bypass line. The bypass line distinguishes the charging device from a previously known single-stage charging device. The bypass valve in this bypass line should be operated unregulated. In other words, the bypass should be opened only under controlled conditions, while the regulation of the charging device takes place via the VTG turbine at each time.
In the case of an exhaust-gas-driven charging device and in other components of a gas conducting system in an internal combustion engine, a flow-blocking component acting as a throttle valve can be arranged in parallel in the gas conducting means. Since the state variables of the gas conducting system are constantly regulated, it is necessary to know the pressure drop over the entire parallel arrangement, which occurs from the two flow-blocking components.
Disclosure of Invention
According to the invention, a method is provided for determining the pressure drop over two parallel-connected flow-blocking components of a turbine of a charging device, in particular driven by exhaust gas, wherein the turbine has a variable turbine geometry and a bypass line with a controllable cross section, and a device and a control system are provided for carrying out the method according to the invention.
Other designs include: determining the pressure drop by applying an approximation method on the basis of the other state variable; the approximation corresponds to an interpolation method using a predetermined interpolation function; giving an upper limit value for a solution of the pressure drop functionAnd a lower limit value by: -equating a normalized first flow function to a normalized second flow function and equating the normalized second flow function to the normalized first flow function, wherein an interpolation is performed between the upper limit value and the lower limit value; selecting the interpolation function as a relative termA monotonic function whereinCorresponding to the total mass flow through the modules arranged in parallel, T corresponding to the temperature on the inlet side, pDsCorresponding to the output pressure on the outlet side, R corresponding to a specific gas constant, A1Corresponding to an effective first flow cross-section through said first component and A2Corresponding to an effective second flow cross-section A through said second component2(ii) a The interpolation function is equivalent toOrAnd x and y correspond to an upper limit value and a lower limit value, and w corresponds to a predefined scaling of the width of the interpolation function; using an interpolation method having the characteristics of monotonicity and fixed point iteration of the function and a derivative of the function on the pressure drop; the pressure drop is determined by means of an iterative solution by: according toUsing the result of the interpolation as a starting value for a fixed-point iteration and in dependence on the slopeInsert it inAndto (c) to (d); the approximation is used only if the ratio of the output pressure to the input pressure at the module is greater than the critical first and second pressure drops as data of the actual pressure drop; if the pressure drop is between the critical first and second pressure drops, the following form is used to determine the pressure drop
Of whereinCorresponding to data on pressure drop as a proportion of output pressure to input pressure, anda first pressure ratio corresponding to a threshold of the first component having a smaller threshold value of the flow function; the further state variable is one or more of the mass flow, the temperature upstream of the component, the pressure downstream of the component, the effective first flow cross section and the effective second flow cross section.
According to a first aspect, a method for determining pressure drop data on a first flow-blocking component and a second flow-blocking component arranged parallel thereto of a turbine of a charging device, in particular driven by exhaust gas, having a variable turbine geometry and a bypass line with a controllable cross section, is provided, comprising the following steps:
-providing a first pressure drop critical for a first flow function of the first component and a second pressure drop critical for a second flow function of the second component;
-predetermining a pressure drop function on the basis of the first and second flow functions and the critical first and second pressure drops;
-determining the pressure drop from the pressure drop function by applying an approximation.
In particular, for exhaust-gas-driven charging devices having a turbine with a variable turbine geometry and a bypass line short-circuiting the turbine, a novel control strategy for controlling the turbine is possible. With such an arrangement, instead of operating the bypass line in a regulated manner, it is possible to control the bypass line only, and the regulation of the charging device takes place at each time by regulating the turbine geometry. In particular in the case of exhaust-gas-driven charging devices having a bypass line, it is necessary to determine the pressure drop over the parallel arrangement in order to set the turbine geometry of the turbine of the exhaust-gas-driven charging device. Knowing the pressure drop, the power of the turbine can be determined, which can be used to characterize the dynamics of the supercharging device. From the pressure drop, the distribution of the mass flow through the branches of the parallel arrangement and thus the turbine power and the exhaust gas temperature downstream of the turbine can be determined. The trajectory of the supercharger speed can thus be calculated given the effective turbine area and bypass area.
In particular for exhaust-gas-driven charging devices with a bypass, the pressure drop with the bypass open depends only on the effective turbine area, which in turn depends on the set turbine geometry.
The pressure drop or the pressure ratio over the parallel arrangement of the components can be determined according to the method described above, if the pressure drop is to be calculated from the effective cross-sectional area of the components.
In the case of conventional regulation of exhaust-gas-driven charging devices with variable turbine geometry without a bypass line, the effect of the turbine bypass is ignored. In this case, although it is also possible to adjust the desired charge pressure statically, charge pressure undershoots and overshoots occur dynamically, since the adjustment only reacts to charge pressure deviations that have already occurred due to changes in the bypass position. Knowing the pressure drop existing across the parallel arrangement, the effect of the opening of the bypass line on the pressure drop can be determined prospectively and the regulation for the turbine geometry can be determined accordingly. In particular, it is thereby possible to suppress charge pressure disturbances due to changes in the effective orifice cross section in the bypass line, since model-based pilot control can already react to changes in the effective orifice cross section in the bypass line.
In particular, further state variables, in particular mass flow, temperature upstream of the component, pressure downstream of the component, effective first flow cross section and/or effective second flow cross section, can be specified, wherein the pressure drop is determined from the further state variables by using an approximation.
Furthermore, the approximation may correspond to an interpolation method using a predetermined interpolation function.
In particular, an upper limit value and a lower limit value can be given to the solution of the pressure drop function by: the normalized first flow function is made equal to the normalized second flow function and the normalized second flow function is made equal to the normalized first flow function, wherein the interpolation is performed between the upper limit value and the lower limit value.
Provision may be made for the interpolation function to be selected relative to the termsA monotonic function whereinCorresponding to the total mass flow, T, through the modules arranged in parallelUsCorresponding to the temperature of the inlet side, pDsCorresponding to the output pressure of the outlet sideForce, R corresponding to a specific gas constant, A1Corresponding to an effective first flow cross-section through said first component and A2Corresponding to an effective second flow cross-section through said second component.
Furthermore, the interpolation function may be equivalent to
Or may for example, as an alternative, correspond to
Wherein the weighting of the values to be interpolated depends on the function variables x and y and w corresponds to a predetermined constant scaling of the width (Breite) of the interpolation function, tanh is the hyperbolic tangent, erf corresponds to the error function。
According to one specific embodiment, the approximation method can be used in particular only when the ratio of the output pressure at the component to the input pressure, as a function of the actual pressure drop, is greater than the critical first and second pressure drops.
Furthermore, the pressure drop can be determined by means of an iterative solution by: using the result of said interpolation as a reference forAnd according to the slopeInsert it inAndin the meantime.
If the pressure drop lies between the critical first and second pressure drops, the following forms can be used in order to determine the pressure drop
Of whereinCorresponding to data (Angabe) on the pressure drop as a proportion of said output pressure to the input pressure, anda first pressure ratio corresponding to a threshold of the first component with a smaller threshold value of the flow function.
According to another aspect, an apparatus for carrying out one of the above-described methods is provided. In particular, the device is configured for:
-providing a first pressure drop critical for a first flow function of the first component and a second pressure drop critical for a second flow function of the second component;
-predetermining said pressure drop function on the basis of said normalized first and second flow functions and critical first and second pressure drops;
-determining the pressure drop from the pressure drop function by applying an approximation.
Drawings
The embodiments are explained in detail below with the aid of the figures. The figures show:
FIG. 1 is a schematic illustration of a parallel arrangement of two components of a gas conducting means acting as throttle valves;
FIG. 2 is a flow chart illustrating a method for calculating a pressure ratio over the parallel arrangement of FIG. 1; and is
FIG. 3 is a graph illustrating an approximation method for determining a pressure ratio over the parallel arrangement of FIG. 1.
Detailed Description
Fig. 1 schematically shows a parallel arrangement 1 of lines for conducting a gaseous medium by means of a first branch line 2 and a second branch line 3. The two branch lines 2, 3 are connected in parallel and each have a component, namely a first flow-blocking component 4 in the first branch line 2 and a second flow-blocking component 5 in the second branch line 3. The flow-blocking assemblies 4, 5 may comprise, for example, simple control valves, variable controllable control valves or turbines having a variably adjustable turbine geometry.
At a mass flow rateAt a temperature TUsAnd an input pressure pUsFeeding gaseous medium to the parallel arrangement and at the same mass flow rateOutput temperature TDsAnd an output pressure pDsThe gaseous medium is conducted away from the parallel arrangement. The mass flow rate generated in the branch lines 2, 3 corresponds to the first mass flow rateAnd a second mass flow rate。
In particular in an application in which the first component 4 of the VTG turbine corresponds to a charging device driven by exhaust gas, it can be determined from the pressure drop that "the flow has an effective first flow cross section a1Or through a second flow cross-section a having an effective cross-section2Second of (2)First and second partial mass flows of the assembly 5、"aspect of division, and from said first portion mass flowDetermining the turbine power P outputTrbAnd the exhaust gas temperature T after the turbineDs. The pressure drop is defined as the pressure ratio So that the magnitude of the pressure drop is smaller when the pressure difference between the output pressure and the input pressure is higher than when the pressure difference is smaller.
The method for determining the pressure ratio is described below in conjunction with the flowchart of FIG. 2.
The following mass flow equation is used as a starting point:
wherein、Is equivalent toThe flow rate functions of the first and second partial lines 2, 3 are different.
With a reduced pressure on the parallel arrangement, the pressure is self-critical when the gas flows through the flow-blocking componentIn contrast, ultrasonic flow may occur. At this point, the flow rate characteristic curveTypically becomes constant and has a value. These two critical values depend on the specific heat c of the gas flowing throughPAnd a specific gas constant R.
By transformation of the equation:
in which a normalized flow function is usedAnd whereinWherein、Is at said critical first or second pressure ratio、Flow through the first or second componentNumerical values of the amounts. Therefore, forIn this case, the application。
For the pressure loss through the turbine of the exhaust-gas-driven charging device, it can be assumed that the functional relationship between mass flow and pressure ratio is the same as for the case when passing through other types of throttle valves, where appropriate for the critical valueAndand (6) carrying out calibration. In general, critical values are predefined for the first and second components 4, 5 in step S1、And、。
in addition, in step S2, the state variable, in particular the mass flow, is providedUpstream of the components 4, 5UsDownstream of the assemblies 4, 5, a pressure pDsEffective first flow cross section A1And an effective second flow cross section A2。
For a turbine having a variable turbine geometry (with flow function)Critical value of) and a turbocharger of a bypass line in which there is an adjustable bypass valve (having a flow function) operating with exhaust gasCritical value of) for the turbine (first component) and the bypass valve (second component) yields:
under the following assumptions:
next, the cases can be distinguished in step S3 into three cases:
the case distinction can be implemented in the following manner:
once the cover is closedPressure ratio greater than the two critical values、One of, the functionStrictly monotonically decreases. This results from the two flow characteristic curvesThe two flow characteristic curves are in a subcritical range (i.e., the flow characteristic curves are in a subcritical range)) Also strictly monotonically decreasing. In the range ofAndinner, the twoIs constantly 1, and thusIs also constant.
From the fixed-point iteration, we derive: as long as the initial valueIs physically meaningful (that is to say that) Then all pairsComprises thatThe contributions of (a) are all real-valued (reelwertig). That is to say that the position of the first electrode,or is largeIs either less than or equal to。
Assumed solution to the fixed-point equationSaid, can be based on said functionThe monotonically decreasing trend of (a) leads to the following conclusion: for any one withPhysical starting value ofIn the case of a composite material, for example,and to have toIn the case of (a) to (b),。
thus, case discrimination can now be implemented by: asUsing said critical first pressure ratioAnd said critical second pressure ratioAnd can thus identify the different uses for the case differentiationThe range of (1). The numerical value of the iteration step thus determines which of the above ranges is within.
In the first case, the two flow characteristic curves do not depend on. Whereby it can be easily calculated in step S4Because ofAndboth become 1. The following applies here:
the same applies to the second case, provided that the flow rate characteristic curve is assumed in step S5In the non-critical range of the flow characteristic curve, the shape is approximately elliptical:
an approximation of an ellipse for the flow characteristic curve is a common approximation. The above-mentioned formula can thus be solved in a simple manner as a quadratic equation in step S6.
For the third case, no algebraic solution exists and therefore an approximate scheme is to be chosen. Since the above-mentioned function can be differentiated and strictly monotonically decreased, not only an iterative solution but also an interpolated solution can be applied. However, the solution of the interpolation has the following advantages: it incurs less computational overhead.
An upper limit and a lower limit can be given to the solution by the above equation by: in step S7To replaceAnd used in the next step S8To replaceThe equation is thus obtained in both cases by being drawn from parenthesis:
in step S9, two approximate solutions can thus be given to the above equation, of which one solution is respectively providedOn top of the exact solution and one solutionUnder the exact solution. This is illustrated in fig. 3, where curve K1 corresponds to
And curve K2 corresponds to:
fixed point equation (Fixpunktgleichung)
Corresponds to the first intersection point SP1 of the curve K1 with a standard straight line and is fixed-point equation
Corresponds to the second intersection point SP2 of the curve K2 with the standard straight line. The solution isNow it can also be obtained by interpolation between the intersection points SP1 and SP 2.
Now, interpolation between the two limits can be performed using a suitable interpolation method in step S10. In this case, the interpolation should depend on the two variables, if differentiation is always possible、Anterior factor of、And should be chosen such that the two preceding factors X are1、X2In the extreme case where one is much smaller than the other preceding factor, the interpolation is always made close to an exact solution. Furthermore, the interpolation function should be strictly monotonically dependent on the two preceding factors X1、X2The difference of (a). From these requirements follows: the interpolation function being preceded by the two preceding factors X1And X2Has a value of 0 or a value of 1 in the extreme case of a relatively large spacing if the interpolation is by the following expression
To express (A), (B) andequivalent to the interpolated solution). Therefore, a corresponding function must be selected in step S11. These requirements are satisfied, for example, by interpolation functions of the following type:
the function variables x and y defining the limit valuesAndwith what weight to enter the interpolation. Here, w corresponds to a scaling of the width of the interpolation function and can be selected appropriately. The accuracy of this approximation can be checked numerically by: solution to interpolationThe exact solution can be determined, for example, in an iterative manner, using a sufficiently large number of iteration steps, with any precision, compared to the exact solution.
Furthermore, provision may be made for the result of the interpolation to be usedUsed as starting value for a suitable iterative method in order to improve the accuracy of the solution. Alternatively, the fixed point characteristic of the above equation may be related to the functionSlope of (2)In combination of (A), (B) and (C)Is equivalent to the functionDerivative of (d). By passingA fixed-point iteration is defined. Because of the fact thatIs always satisfied in the non-critical range, so that
and thenUpper and lower limits are given for the solution of the above equation. Using said slopeTo obtain a solution of the above equationRelative toAndin betweenThe range of relative positions (Ma β).The larger the size of the tube is,the closer to。The closer to zero the more closely,the closer to. If it is notHas a value of-1, thenIs substantially centered.
Thus, again, the values may be interpolated by suitable interpolationAndinterpolation is performed in between. Suitably means that the above requirements are met in this case with a biased parameterization of the interpolation function:
Claims (13)
1. (pressure drop) across a first flow-blocking module (4) and a second flow-blocking module (5) arranged in parallel thereto for the turbine of a supercharging device driven by exhaust gas) Method for determining, the turbine having a variable turbine geometry and a bypass line with a controllable cross section, the method comprising the following steps:
-providing a first flow function (f) for the first component (4)) Critical first pressure drop of (c) (() And a second flow function for the second component (5) (() Critical second pressure drop of (c) (();
-at normalized first and second flow functions (c:)) And critical first and second pressure drops () A pressure drop function is preset on the basis of the pressure drop;
3. A method as claimed in claim 1 or 2, wherein the approximation corresponds to an interpolation using a predetermined interpolation function.
4. A method according to claim 3, wherein upper and lower limit values for the solution of said pressure drop function are given by: normalized first flow function () A second flow function equal to the normalization (a)) And a second flow function (f) normalizing said second flow) Equal to the normalized first flow function () Wherein an interpolation is performed between the upper limit value and the lower limit value.
5. The method according to claim 4, wherein said interpolation function is selected (S11) as a relative termA monotonic function whereinCorresponding to the total mass flow through the modules arranged in parallel, T corresponding to the temperature on the inlet side, pDsCorresponding to the output pressure on the outlet side, R corresponding to a specific gas constant, A1Corresponding to an effective first flow cross section through the first component (4) and A2Corresponding to an effective second flow cross section A through the second component (5)2。
8. The method according to claim 3, wherein the pressure drop is determined by means of an iterative solution method () The method comprises the following steps: according toUsing the result of the interpolation as a starting value for a fixed-point iteration and in dependence on the slopeInsert it inAndin the meantime.
10. The method of claim 1 or 2, wherein if said pressure drop is critical first and second pressure drops (f &)) In order to determine the pressure drop, the following form is used
12. Apparatus for carrying out one of the methods according to any one of claims 1 to 11.
13. A machine-readable storage medium, on which a computer program is stored, which computer program is designed to carry out all the steps of the method according to any one of claims 1 to 11.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102015216255.9 | 2015-08-26 | ||
DE102015216255.9A DE102015216255A1 (en) | 2015-08-26 | 2015-08-26 | Method for calculating a pressure drop over two flow-inhibiting components connected in parallel in a gas guidance system, in particular in an exhaust-driven charging device for an internal combustion engine |
Publications (2)
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US20120151999A1 (en) * | 2010-12-18 | 2012-06-21 | GM Global Technology Operations LLC | Method for ascertaining a flap position of an exhaust gas heat exchanger |
EP2479409A1 (en) * | 2011-01-25 | 2012-07-25 | Peugeot Citroën Automobiles SA | Method for controlling the temperature of exhaust gases in order to optimise the regeneration of a particle filter |
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DE102013109551A1 (en) * | 2012-09-04 | 2014-03-06 | General Electric Company | Methods and systems for preventing exhaust overheating |
WO2014193333A1 (en) * | 2013-05-25 | 2014-12-04 | International Engine Intellectual Property Company, Llc | Upstream nox estimation |
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JP5553243B2 (en) * | 2011-11-01 | 2014-07-16 | 株式会社豊田自動織機 | Exhaust gas purification device for internal combustion engine |
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CN102452387A (en) * | 2010-11-02 | 2012-05-16 | 福特全球技术公司 | Vehicle launch anticipation and adaptation |
US20120151999A1 (en) * | 2010-12-18 | 2012-06-21 | GM Global Technology Operations LLC | Method for ascertaining a flap position of an exhaust gas heat exchanger |
EP2479409A1 (en) * | 2011-01-25 | 2012-07-25 | Peugeot Citroën Automobiles SA | Method for controlling the temperature of exhaust gases in order to optimise the regeneration of a particle filter |
US20130074494A1 (en) * | 2011-09-25 | 2013-03-28 | John N. Chi | System and method for estimating engine exhaust manifold operating parameters |
DE102013109551A1 (en) * | 2012-09-04 | 2014-03-06 | General Electric Company | Methods and systems for preventing exhaust overheating |
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