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Introduction 19 generated in numerical format and are solved directly using numerical integration routines embedded in the package. The second and more recent type of MBS program identified formulates the equations in symbolic form and often uses an independent solver. The authors also describe toolkits as collections of routines that generate models, formulate and solve equations, and present results. The VDAS system is identified as falling into this category of computer software used for vehicle dynamics. Other examples of more recently developed codes formulate the equations algebraically and use a symbolic approach. Examples of these programs include MESA VERDE (Wittenburg and Wolz, 1985), AUTOSIM (Sayers, 1990), and RASNA Applied Motion Software (Austin and Hollars, 1992). Crolla (Crolla et al., 1992) provides a summary comparison of the differences between numeric and symbolic code. As stated MBS programs will usually automatically formulate and solve the equations of motion although in some cases such as with the work described by Costa (1991) and Holt (Holt and Cornish, 1992; Holt, 1994) a program SDFAST has been used to formulate the equations of motion in symbolic form and another program ACSL (Automatic Continuous Simulation Language) has been used to generate a solution. Special-purpose programs are designed and developed with the objective of solving only a specific set of problems. As such they are aimed at a specific group of problems. A typical example of this type of program would be AUTOSIM described by Sayers (1990, 1992), Sharp (1997) and Mousseau et al. (1992) which is intended for vehicle handling and has been developed as a symbolic code in order to produce very fast simulations. Programs such as this can be considered to be special purpose as they are specifically developed for a given type of simulation but do, however, allow flexibility as to the choice and complexity of the model. An extension of this is where the equations of motion for a fixed vehicle modelling approach are programmed and cannot be changed by the user such as the HVOSM (Highway-Vehicle-Object Simulation Model) developed at the University of Michigan Transport Research Institute (UMTRI) (Sayers, 1992). The program includes tyre and suspension models and can be used for impact studies in addition to the normal ride and handling simulations. Crolla et al. (1992) indicate that the University of Missouri has also developed a light vehicle dynamics simulation (LVDS) program that runs on a PC and can produce animated outputs. In the mid-1980s Systems Technology Inc. developed a program for vehicle dynamics analysis nonlinear (VDANL) simulation. This program is based on a 13 degree of freedom, lumped parameter model (Allen et al., 1987) and has been used by researchers at Ohio State University for sensitivity analysis studies (Tandy et al., 1992). The modelling of the tyre forces and moments at the tyre to road contact patch is one of the most complex issues in vehicle handling simulation. The models used are not predictive but are used to represent the tyre force and moment curves typically found through laboratory or road-based rig testing of a tyre. Examples of tyre models used for vehicle handling discussed in this book include: (i) A sophisticated tyre model known as the ‘Magic Formula’. This tyre model has been developed by Pacejka and his associates (Bakker et al.,
20 Multibody Systems Approach to Vehicle Dynamics 1986, 1989; Pacejka and Bakker, 1993) and is known to give an accurate representation of measured tyre characteristics. The model uses modified trigonometric functions to represent the shape of curves that plot tyre forces and moments as functions of longitudinal slip or slip angle. In recent years the work of Pacejka has become well known throughout the vehicle dynamics community. The result of this is a tyre model that is now widely used both by industry and academic institutions and is undergoing continual improvement and development. The complexity of the model does, however, mean that well over 50 or more parameters may be needed to define a tyre model and that software must be obtained or developed to derive the parameters from measured test data. (ii) The second model considered here is known as the Fiala tyre model (Fiala, 1954) and is provided as the default tyre model in MSC.ADAMS. This is a much simpler model that also uses mathematical equations to represent the tyre force and moment characteristics. Although not so widely recognized as Pacejka’s model the fact that this model is the default in MSC.ADAMS and is simpler to use led to its inclusion. The advantage of this model is that it only requires 10 parameters and that the physical significance of each of these is easy to comprehend making this a good starting point for students and newcomers to the discipline. The parameters can also be quickly and easily derived from measured test data without recourse to special software. It should also be noted, however, that this model unlike Pacejka’s is not suitable for combined braking and cornering and can only be used under pure slip conditions. The Fiala formulation also has some limitations at high slip angles and is thus unsuitable for limit manoeuvres even when pure slip conditions are included. (iii) The fourth modelling approach is to use a straightforward interpolation model. This was the original tyre modelling method used in MSC.ADAMS (Ryan, 1990). This methodology is still used by some companies but has, to a large extent, been superseded by more recent parameter-based models. The method is included here as a useful benchmark for the comparison of other tyre models in Chapter 5. Another tyre model is provided for readers as a source listing in Appendix B. This model (Blundell, 2003) has been developed by Harty and as with the Fiala model has the advantage of requiring only a limited number of input parameters. The implementation is more complete, however, than the Fiala model and includes representation of the following: ● ● ● ● Comprehensive slip Load dependency Camber thrust Post limit It has been found that the Harty model is robust when modelling limit behaviour including, for example, problems involving low grip or prolonged wheelspin.
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20 Multibody Systems Approach to Vehicle Dynamics<br />
1986, 1989; Pacejka and Bakker, 1993) and is known to give an accurate<br />
representation of measured tyre characteristics. The model uses modified<br />
trigonometric functions to represent the shape of curves that plot tyre<br />
forces and moments as functions of longitudinal slip or slip angle. In recent<br />
years the work of Pacejka has become well known throughout the vehicle<br />
dynamics community. The result of this is a tyre model that is now widely<br />
used both by industry and academic institutions and is undergoing continual<br />
improvement and development. The complexity of the model does,<br />
however, mean that well over 50 or more parameters may be needed to define<br />
a tyre model and that software must be obtained or developed to derive the<br />
parameters from measured test data.<br />
(ii) The second model considered here is known as the Fiala tyre model<br />
(Fiala, 1954) and is provided as the default tyre model in MSC.ADAMS.<br />
This is a much simpler model that also uses mathematical equations to represent<br />
the tyre force and moment characteristics. Although not so widely<br />
recognized as Pacejka’s model the fact that this model is the default in<br />
MSC.ADAMS and is simpler to use led to its inclusion. The advantage of<br />
this model is that it only requires 10 parameters and that the physical significance<br />
of each of these is easy to comprehend making this a good starting<br />
point for students and newcomers to the discipline. The parameters can<br />
also be quickly and easily derived from measured test data without recourse<br />
to special software. It should also be noted, however, that this model unlike<br />
Pacejka’s is not suitable for combined braking and cornering and can only<br />
be used under pure slip conditions. The Fiala formulation also has some<br />
limitations at high slip angles and is thus unsuitable for limit manoeuvres<br />
even when pure slip conditions are included.<br />
(iii) The fourth modelling approach is to use a straightforward interpolation<br />
model. This was the original tyre modelling method used in MSC.ADAMS<br />
(Ryan, 1990). This methodology is still used by some companies but has,<br />
to a large extent, been superseded by more recent parameter-based models.<br />
The method is included here as a useful benchmark for the comparison of<br />
other tyre models in Chapter 5.<br />
Another tyre model is provided for readers as a source listing in Appendix<br />
B. This model (Blundell, 2003) has been developed by Harty and as with<br />
the Fiala model has the advantage of requiring only a limited number of<br />
input parameters. The implementation is more complete, however, than the<br />
Fiala model and includes representation of the following:<br />
●<br />
●<br />
●<br />
●<br />
Comprehensive slip<br />
Load dependency<br />
Camber thrust<br />
Post limit<br />
It has been found that the Harty model is robust when modelling limit behaviour<br />
including, for example, problems involving low grip or prolonged<br />
wheelspin.