4569846498
Modelling and assembly of the full vehicle 365 Translational joint to ground Steering rack part TRANS MOTION Steering motion inputs applied at the rack to ground translational joint Front suspension INPLANE TRANS MOTION Fig. 6.39 Front suspension steering ratio test model Toe out – road wheel steer (deg) – toe in 10.0 8.0 6.0 4.0 2.0 0.0 2.0 4.0 6.0 8.0 FRONT RIGHT SUSPENSION – STEERING RATIO TEST 100 mm rebound _ _ _ _ _ _ _ _ Static position _______________ 100 mm bump ___ ___ ___ ___ 10.0 150.0 90.0 30.0 30.0 90.0 150.0 180.0 120.0 60.0 0.0 60.0 120.0 180.0 Left turn – steering wheel angle (deg) – right turn Fig. 6.40 Results of steering ratio test for MSC.ADAMS front right suspension model In the following example the geometric ratio between the rotation of the steering column and the travel of the rack is already known, so it is possible to apply a motion input at the rack to ground joint that is equivalent to handwheel rotations either side of the straight ahead position. The jack part shown in Figure 6.39 can be used to set the suspension height during
366 Multibody Systems Approach to Vehicle Dynamics a steering test simulation. Typical output is shown in Figure 6.40 where the steering wheel angle is plotted on the x-axis and the road wheel angle is plotted on the y-axis. The three lines plotted represent the steering ratio test for the suspension in the static (initial model set up here), bump and rebound positions. Having decided on the suspension modelling strategy and how to manage the relationship between the handwheel rotation and steer change at the road wheels the steering inputs from the driver and the manoeuvre to be performed need to be considered. 6.12.3 Steering inputs for vehicle handling manoeuvres The modelling of steering inputs suggests for the first time some representation of the driver as part of the full vehicle system model. Any system can be considered to consist of three elements – the ‘plant’ (the item to be controlled), the input to the plant and the output from the plant (Figure 6.41). Inputs to the system (i.e. handwheel inputs) are referred to as ‘open loop’ or ‘closed loop’. An open loop steering input requires a time dependent rotation to be applied to the part representing a steering column or handwheel in the simulation model. In the absence of these bodies an equivalent translational input can be applied to the joint connecting a rack part to the vehicle body or chassis, assuming a suspension linkage modelling approach has been used. Examples will be given here where the time dependent motion is based on a predetermined function or equation to alter the steering inputs or a series of measured inputs from a vehicle on the proving ground. Any system can be considered to consist of three elements – the ‘plant’ (the item to be controlled), the input to the plant and the output from the plant (Figure 6.41). When a closed-loop controller is added to the system, its goal is to allow the input to the plant to be adjusted so as to produce the desired output. The desired output is referred to as the ‘reference’ state; a difference between the actual output and the reference is referred to as an ‘error’ state. The goal of the control system is to drive the error to zero. We can consider an example of a closed loop steering input that requires a torque to be applied to the handwheel or steering column such that the vehicle will follow a predetermined path during the simulation. A mechanism must be modelled to measure the deviation of the vehicle from the path and process this in a manner that feeds back to the applied steering torque. Error Input Reference Plant Output Gain Fig. 6.41 grey Feedback An open-loop system, in black, is a subset of a closed-loop system, in
- Page 338 and 339: Tyre characteristics and modelling
- Page 340 and 341: Tyre characteristics and modelling
- Page 342 and 343: Tyre characteristics and modelling
- Page 344 and 345: Tyre characteristics and modelling
- Page 346 and 347: Tyre characteristics and modelling
- Page 348 and 349: Tyre characteristics and modelling
- Page 350 and 351: Modelling and assembly of the full
- Page 352 and 353: Modelling and assembly of the full
- Page 354 and 355: Modelling and assembly of the full
- Page 356 and 357: Modelling and assembly of the full
- Page 358 and 359: Modelling and assembly of the full
- Page 360 and 361: Modelling and assembly of the full
- Page 362 and 363: Modelling and assembly of the full
- Page 364 and 365: Modelling and assembly of the full
- Page 366 and 367: Modelling and assembly of the full
- Page 368 and 369: Modelling and assembly of the full
- Page 370 and 371: Modelling and assembly of the full
- Page 372 and 373: Modelling and assembly of the full
- Page 374 and 375: Modelling and assembly of the full
- Page 376 and 377: Modelling and assembly of the full
- Page 378 and 379: Modelling and assembly of the full
- Page 380 and 381: Modelling and assembly of the full
- Page 382 and 383: Modelling and assembly of the full
- Page 384 and 385: Modelling and assembly of the full
- Page 386 and 387: Modelling and assembly of the full
- Page 390 and 391: Modelling and assembly of the full
- Page 392 and 393: Modelling and assembly of the full
- Page 394 and 395: Modelling and assembly of the full
- Page 396 and 397: Modelling and assembly of the full
- Page 398 and 399: Modelling and assembly of the full
- Page 400 and 401: Modelling and assembly of the full
- Page 402 and 403: Modelling and assembly of the full
- Page 404 and 405: Modelling and assembly of the full
- Page 406 and 407: Modelling and assembly of the full
- Page 408 and 409: Modelling and assembly of the full
- Page 410 and 411: Modelling and assembly of the full
- Page 412 and 413: Modelling and assembly of the full
- Page 414 and 415: Modelling and assembly of the full
- Page 416 and 417: Modelling and assembly of the full
- Page 418 and 419: 7 Simulation output and interpretat
- Page 420 and 421: Simulation output and interpretatio
- Page 422 and 423: Simulation output and interpretatio
- Page 424 and 425: down and even more difficult to asc
- Page 426 and 427: Simulation output and interpretatio
- Page 428 and 429: Simulation output and interpretatio
- Page 430 and 431: Simulation output and interpretatio
- Page 432 and 433: Simulation output and interpretatio
- Page 434 and 435: Simulation output and interpretatio
- Page 436 and 437: Simulation output and interpretatio
Modelling and assembly of the full vehicle 365<br />
Translational joint<br />
to ground<br />
Steering rack<br />
part<br />
TRANS<br />
MOTION<br />
Steering motion inputs<br />
applied at the rack to<br />
ground translational joint<br />
Front<br />
suspension<br />
INPLANE<br />
TRANS<br />
MOTION<br />
Fig. 6.39<br />
Front suspension steering ratio test model<br />
Toe out – road wheel steer (deg) – toe in<br />
10.0<br />
8.0<br />
6.0<br />
4.0<br />
2.0<br />
0.0<br />
2.0<br />
4.0<br />
6.0<br />
8.0<br />
FRONT RIGHT SUSPENSION – STEERING RATIO TEST<br />
100 mm rebound<br />
_ _ _ _ _ _ _ _<br />
Static position _______________<br />
100 mm bump ___ ___ ___ ___<br />
10.0<br />
150.0 90.0 30.0 30.0 90.0 150.0<br />
180.0 120.0 60.0 0.0 60.0 120.0 180.0<br />
Left turn – steering wheel angle (deg) – right turn<br />
Fig. 6.40 Results of steering ratio test for MSC.ADAMS front right<br />
suspension model<br />
In the following example the geometric ratio between the rotation of the<br />
steering column and the travel of the rack is already known, so it is possible<br />
to apply a motion input at the rack to ground joint that is equivalent<br />
to handwheel rotations either side of the straight ahead position. The jack<br />
part shown in Figure 6.39 can be used to set the suspension height during