Abstract:
A method and an apparatus for simulating the operation of a pressured air source or sink such as a compressor or a turbine for a vehicle internal combustion engine calculates momentum sources at interfaces in the compressor or the turbine. A model stores steady state values of mass flux and enthalpy change related to rotational speed, inlet pressure and temperature and outlet pressure. The simulation can be an input to an engine control module for controlling the operation of the vehicle engine connected with the compressor or turbine.

Description:
BACKGROUND OF THE INVENTION  
       [0001]     The present invention relates generally to an apparatus and a method for simulating turbine and compressor performance and, in particular, to such use in engine modeling and control.  
         [0002]     One-dimensional Computational fluid dynamics (CFD) codes are used to calculate fluid flow in many types of internal combustion engines. These codes use a gas dynamic model for predicting the gas flows in an engine. The approach is described in John B. Heywood, “Internal Combustion Engine Fundamentals”, pp. 756-762. In these CFD codes, compressor and turbine performance maps are typically used to impose a steady state mass flow rate.  
         [0003]     Various examples of modeling and uses of look up tables for control are provided in the following documents:  
         [0004]     The U.S. Pat. No. 5,526,266 discloses a method for diagnosing an engine using a computer based boost pressure model that compares actual measured boost pressure values from a turbocharger with modeled boost pressure values.  
         [0005]     The U.S. Pat. No. 5,753,805 discloses a method for determining pneumatic states in an internal combustion engine system that utilizes look up tables in determining pressure and temperature density corrections for mass flow calculations.  
         [0006]     The U.S. Pat. No. 5,915,917 discloses a compressor stall and surge control using airflow asymmetry measurement. Asymmetry function is measured by static pressure sensors or total pressure sensors located along the circumference of the compressor inlet, which provides pressure signals to a signal processor.  
         [0007]     The U.S. Pat. No. 6,098,010 discloses a method and apparatus for predicting and stabilizing compressor stall that utilizes axial velocity measurements as a function of time to predict stall.  
         [0008]     The U.S. Pat. No. 6,178,749 discloses a method of reducing turbo lag in diesel engines having exhaust gas recirculation that generates a turbocharger control signal based on actual and modeled intake manifold absolute pressure and mass airflow values.  
         [0009]     The U.S. Pat. No. 6,298,718 discloses a turbocharger compressor diagnostic system wherein sensor data is verified with a “rationality test” and then compared to a compressor operation map to determine if the compressor is in surge or choke.  
         [0010]     The U.S. Pat. No. 6,510,691 discloses a method for regulating or controlling a supercharged internal combustion engine having a turbocharger with variable turbine geometry that utilizes upper and lower ranges based on different operating states to determine the required adjustments for the variable geometry of the turbocharger.  
         [0011]     The published U.S. Patent Application No. 2003/0101723 discloses a method for controlling a charge pressure in an internal combustion engine with an exhaust gas turbocharger that calculates a manipulated variable by comparing the power or torque or a compressor with a power or torque loss occurring in transmission from a turbine to the compressor and then utilizes the manipulated variable to set the charge pressure output of the compressor.  
         [0012]     The published U.S. Patent Application No. 2003/0106541 discloses a control system for an internal combustion engine boosted with an electronically controlled compressor that utilizes lookup tables or factors that are combined to generate low and high idle speed factors for the compressor.  
         [0013]     The published U.S. Patent Application No. 2003/0216856 discloses diagnostic systems for turbocharged engines that utilize inputs from a plurality of sensors provided to an engine control module to determine performance of the turbocharger based on predicted versus actual value in comparison to stored compressor and turbine maps.  
         [0014]     The published U.S. Patent Application No. 2005/0131620 discloses a control system that utilizes a predictive model, a control algorithm, and a steady state map having look-up tables for controlling boost and exhaust gas recirculation (EGR) valve operation of a diesel engine.  
         [0015]     The U.S. Pat. No. 3,738,102 discloses a fuel control for turbine type power plant having variable area geometry that controls the turbine by determining a “APIP” value and the U.S. Pat. No. 5,381,775 discloses a system for controlling an internal combustion engine that includes a controller receiving a signal from a summation point that is in communication with a characteristics map and a simulation.  
       SUMMARY OF THE INVENTION  
       [0016]     The present invention concerns an apparatus and method for utilizing momentum in determining performance of a turbine or compressor.  
         [0017]     Instead of imposing a steady state mass flow rate, pressure ratio or outlet pressure, as previously done, this method imposes a steady state momentum source derived from the map.  
         [0018]     One advantage over existing technology is that it introduces a physically based aerodynamic time lag, so that the dynamic behavior of the compressor or turbine may be better represented. This can improve acoustical predictions, and predictions of performance under pulsed flow conditions.  
         [0019]     Other methods for modeling surging compressor systems such as the Greitzer model (Greitzer, E. M., “Surge and Rotating Stall in Axial Flow Compressors Part1: Theoretical Compression System Model”, Transactions of ASME, p. 190, April, 1976) are not applicable to a one-dimensional (cfd) gas dynamics approach.  
         [0020]     Near the surge limit of a compressor map, curves of pressure ratio (Outlet pressure divided by inlet pressure) verses mass flow at constant speed often have a positive slope, so that the peak pressure ratio occurs at a mass flow rate higher than the map surge limit mass flow rate. This makes it difficult to use the pressure ratio in order to look up a mass flow from the map, because for a given pressure ratio, there can be more than one mass flow. This new method can be used to calculate a unique value for the mass flow.  
         [0021]     The “Momentum Volume junction” configuration allows the model to include the aerodynamic effects of the volume of the turbine or compressor, and it creates an interior area that can be used for heat transfer modeling to be implemented as well.  
         [0022]     The apparatus and method according to the present invention can be used by any manufacturer of turbocharged, supercharged or turbo compounded internal combustion engines to improve the design process and actual engine control. 
     
    
     DESCRIPTION OF THE DRAWINGS  
       [0023]     The above, as well as other, advantages of the present invention will become readily apparent to those skilled in the art from the following detailed description of a preferred embodiment when considered in the light of the accompanying drawings in which:  
         [0024]      FIG. 1  is a graph of fluid flow momentum versus position relative to an interface;  
         [0025]      FIG. 2  is schematic view of a simple momentum junction configuration that can be modeled according to the present invention;  
         [0026]      FIG. 3  is a schematic view of volume momentum junction configuration that can be modeled according to the present invention; and  
         [0027]      FIG. 4  is a block diagram of an engine control system in accordance with the present invention. 
     
    
     DESCRIPTION OF THE PREFERRED EMBODIMENT  
       [0028]     Typically, devices such as compressors are used to increase combustion engine performance by compressing the inlet air. Devices such as turbines are typically used to extract energy from the exhaust gases. The energy extracted by the turbine can be used to drive a compressor (as in a turbocharger) or to provide power for other purposes, such as driving an auxiliary device, or to add mechanical power to the engine output.  
         [0029]     The present invention concerns a turbine or compressor simulation model that utilizes mass flows, enthalpy rise or drop and junction (compressor or turbocharger) to calculate momentum source at the inlets and outlets. The simulation model is intended to improve the prediction of turbine and compressor performance under conditions of pulsed flow, to improve the modeling of compressor surge stability, to compute mass flow when it is not uniquely defined by the inlet and outlet pressures, and to improve the prediction of pressure wave transmission, while using look up maps to represent the steady state performance, in a CFD code.  
         [0030]     Since the method according to the present invention can be used similarly for either a compressor or a turbine, both a compressor and a turbine will be referred to as a “junction” in the following description.  
         [0031]     In the prior art algorithm that is typically used for turbine or compressor performance in a simulation, a map of the steady state performance is used to characterize the turbine or compressor. The map typically relates the values of pressure ratio, inlet pressure, inlet temperature, speed and mass flow, and efficiency or enthalpy rise that occur under steady state conditions. The maps can be typically represented by Equation 1 or 2 wherein “ss” represents “steady state”. 
 
{dot over (m)} ss , Δh ss =f(N, P inlet , T inlet , P outlet )   Equation 1 
 
 or 
 
P outletss , Δh ss =f(N, P inlet , T inlet , {dot over (m)} ss )   Equation 2 
 
         [0032]     In this new approach, rather than prescribing the instantaneous mass flow, pressure, pressure ratio, or enthalpy rise as steady state values looked up from the maps, a momentum source is calculated and used in the solution of the control surface or volume representing the turbine or compressor. This momentum source is the force that would be exerted on the fluid by the impeller or vanes in the turbine or compressor and is chosen such that in the steady state the mass flow, and/or the outlet pressure, and/or the enthalpy rise will match the steady state values looked up from the map. With this methodology, a physical model for the steady state behavior of the compressor or turbine or one of its components, such as the rotor or a stator, could also be used in the place of a map.  
         [0000]      FIG. 1 , Momentum Balance Across Interface:  
         [0033]     The momentum balance for a particular discretization mesh configuration is shown in  FIG. 1 . This method could be applied with any discretization mesh however. In this configuration, u denotes an upstream control volume, d denotes a downstream control volume and i denotes an interface between the upstream and downstream control volumes. {dot over (m)} is a mass flux, U is a velocity, P is a static pressure, A i  is the interface area, and S i  is the momentum source. A positive mass flux or velocity goes from upstream to downstream, and a negative mass flux or velocity goes from downstream to upstream. At the interface i, the mass flux at the time step n+1 is calculated from a momentum balance with Equation 3.  
                 m   .     i     n   +   1       =         m   .     i     +       [           m   .     u     ⁢     U   u       -         m   .     d     ⁢     U   d       +       A   i     ⁡     (       P   u     -     P   d       )       +     S   i       ]         Δ   ⁢           ⁢   t         Δ   ⁢           ⁢   u     +     Δ   ⁢           ⁢   d                     Equation   ⁢           ⁢   3             
 
 In the steady state condition,  
             0   =       [           m   .     u     ⁢     U   u       -         m   .     d     ⁢     U   d       +       A   i     ⁡     (       P   u     -     P   d       )       +     S   i       ]         Δ   ⁢           ⁢   t         Δ   ⁢           ⁢   u     +     Δ   ⁢           ⁢   d                   Equation   ⁢           ⁢   4             or                           S   i     =         m   .     ⁡     (       U   d     -     U   u       )       +       A   i     ⁡     (       P   d     -     P   u       )                 Equation   ⁢           ⁢   5             
 
         [0034]     In Equation 5, some or all of U d , U u , P d  and P u  and {dot over (m)} are steady state values taken from, or derived from the left hand side of Equation 1. The remaining terms are instantaneous values.  
         [0000]     Possible Solution Configurations:  
         [0035]     There are two basic configurations possible, the ‘momentum control surface’, and the ‘momentum control volume’. The momentum control surface is shown in  FIG. 2 .  
         [0000]      FIG. 2 , Momentum Control Surface:  
         [0036]     This configuration has no internal volume. It connects adjacent computational cells and calculates the momentum balance described by Equation 3 at the interface. In this case, the upstream quantities are the inlet quantities, and the downstream quantities are the outlet quantities.  
         [0037]     The momentum control volume is shown in  FIG. 3 . This configuration has an internal volume. A momentum balance is performed for each inlet or outlet interface. The figure shows a control volume with one outlet and two inlets, but any number of inlets or outlets is possible.  
         [0000]      FIG. 3 , Momentum Volume Junction:  
         [0038]     The momentum control surface is simple, numerically robust, and requires few input parameters. The momentum control volume configuration has the advantage of supporting multiple inlets and/or outlets, and also internal volume can be used to represent dynamic behavior of the volume inside the actual compressor or turbine.  
       ILLUSTRATIVE EXAMPLE 1  
       [0039]     One possible instance of this algorithm, for the momentum control surface shown in  FIG. 2 , could be as follows.  
         [0040]     From the map, look up the steady state outlet pressure P outletss , and enthalpy rise or loss Δh ss  from the instantaneous values of speed N, upstream pressure P u , upstream temperature T u , and from the instantaneous {dot over (m)} as flow m as shown in Equation 6. 
 
P outletss , Δh ss =f(N, P u , T u , {dot over (m)})   Equation 6 
 
 The momentum source could then be calculated as: 
 
S i ={dot over (m)}(U d −U)+A i (P outless −P u )   Equation 7 
 
         [0041]     In Equation 6, U d , and U u  are instantaneous upstream and downstream velocities. The momentum source in Equation 7 is the force that would be required exerted on the fluid by the interface, in order for the outlet pressure to be the steady state pressure from the map, given the instantaneous upstream pressure upstream and downstream velocities, and mass flow.  
         [0042]     In Equation 3, if we assume that the upstream and downstream mass flows are the same, then if Equation 6 is substituted into Equation 3,  
                 m   .     i     n   +   1       =         m   .     i     +       [       A   i     ⁡     (       P   outletss     -     P   d       )       ]         Δ   ⁢           ⁢   t         Δ   ⁢           ⁢   u     +     Δ   ⁢           ⁢   d                     Equation   ⁢           ⁢   8             
 
         [0043]     For a compressor, or any other junction in which the mass flow is not a unique function of the pressure ratio, Equations 7 and 8 can be used to uniquely calculate the mass flow.  
         [0044]     The length Δu+Δd can be a characteristic length of the flow path through the junction. For a compressor, for example:  
                 m   .     i     n   +   1       =         m   .     i     +       [       A   i     ⁡     (       P   outletss     -     P   d       )       ]         Δ   ⁢           ⁢   t       L   c                   Equation   ⁢           ⁢   9             
 
         [0045]     Where L c  is the characteristic length of the compressor. The length L c , along with the cross sectional area define a time constant for the compressor. The time lag caused by the momentum balance of Equation 9 makes it possible to characterize the surge stability of the compressor.  
       ILLUSTRATIVE EXAMPLE 2  
       [0046]     Another possible instance of this algorithm, for the momentum control surface shown in  FIG. 2 , could be as follows.  
         [0047]     In Equation 5, the mass flow, velocity and pressure terms are replaced by steady state values to obtain Equation 10 
 
S i ={dot over (m)} ss (U dss −U uss )+A(P outlet −P inlet )   Equation 10 
 
         [0048]     The momentum source in Equation 11 is the force that would be exerted on the fluid by the momentum control surface, if it were in steady state. Assume that in the map, from Equation 1 P inlet  and T inlet  are a static temperature and pressure, and that P outlet  is a static pressure.  
         [0049]     The inlet velocity,  
               U   uss     =           m   .     ss     ⁢   R   ⁢           ⁢     T   inlet           P   inlet     ⁢     A   u                 Equation   ⁢           ⁢   11             
 
 where R is the ideal gas law constant for the working fluid. 
 
         [0050]     The outlet stagnation temperature can be calculated as:  
               T   Ooutlet     =       T   Ooutlet     +       Δ   ⁢           ⁢     h   ss         C   p                 Equation   ⁢           ⁢   12             
 
 Where C p  is the specific heat of the working fluid. 
 
         [0051]     The static and stagnation temperatures can be related by using the mass flow and Mach number relationships. 
 
 The outlet velocity is then:  
               U   oss     =           m   .     ss     ⁢   R   ⁢           ⁢     T   outlet           P   outlett     ⁢     A   d                 Equation   ⁢           ⁢   13             
 
         [0052]     A computer running a software program can be used in an engine control system to predict the dynamic behavior of the volume inside the actual compressor or turbine and achieve better control of the engine. In  FIG. 4 , there is shown a model  40  representing such a computer and software.  
         [0053]     Also shown in  FIG. 4  is an engine control system  70  according to the present invention. An internal combustion engine  72  is provided with an intake manifold  74  and an exhaust manifold  76 . In some engines, a throttle (not shown) controls the amount of fresh air admitted to the engine  72 .  
         [0054]     Some engines have one or more compressors  78 . The compressor may be of a variable geometry type, in which case the flow characteristics can be controlled. The compressor may be driven by an exhaust turbine  95 , or it can be driven by another power source such as the engine crank shaft. Also, the engine may have one or more of the exhaust turbines  95 . The exhaust gas flow through the turbine  95  may be controlled by a waste gate, or the turbine  95  may be of the variable geometry type. The turbine  95  may be used to drive a compressor, or it may be used to add power to the engine output, or to drive an auxiliary device. The waste gate, and or variable geometry settings of the compressor and/or the turbine respond to control signals from the engine control module (ECM)  84 .  
         [0055]     In an engine with exhaust gas recirculation (EGR), a small portion of the exhaust gas flowing out of the engine  72  through the exhaust manifold  76  is returned to the intake manifold  74  through a passage  80  connected between the manifolds. The amount of the exhaust gas recirculated is controlled by adjusting an EGR valve  82 . The valve  82  responds to a control signal from an engine ECM  84  connected to the valve. The ECM  84  also is connected to a fuel control  86  to generate a control signal to determine the amount of fuel delivered to the engine  72 .  
         [0056]     The ECM  84  receives sensor signals from a plurality of sensors  92  that provide information about the operating conditions of the engine  72  and the emission control system  70 . For example, the sensors  92  can include a mass air flow sensor (MAF), an intake manifold absolute pressure sensor (MAP), a throttle position sensor (TPS), a vehicle speed sensor (VSS), an engine RPM sensor (RPM), a temperature of coolant sensor (TMP), a heated exhaust gas oxygen sensor (HEGO), an exhaust gas temperature sensor (EGT) and a catalyst monitoring sensor (CMS). Typically, the HEGO sensor is located in the exhaust gas stream upstream of the inlet to the converter  90 , the EGT sensor is located in the converter, and the CMS is located downstream of the outlet from the converter.  
         [0057]     The ECM  84  also is connected to the model  40  to provide data thereto and receive control direction therefrom. The ECM  84  can control the compressor  78  or the  30  turbine  95  based upon the estimated or simulated performance generated by the model  40 . The control is typically achieved by modulating the turbine waste gate, or the compressor or turbine variable geometry controls. Other means of control may be used as well, such as bypass valves in the intake or exhaust ducting. Thus, the engine control system  70  according to the present invention is a model-based realtime engine control.  
         [0058]     In accordance with the provisions of the patent statutes, the present invention has been described in what is considered to represent its preferred embodiment. However, it should be noted that the invention can be practiced otherwise than as specifically illustrated and described without departing from its spirit or scope.