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English Pages 523 Year 2005
Uwe Kiencke Lars Nielsen Automotive Control Systems For Engine, Driveline, and Vehicle
Uwe Kiencke Lars Nielsen
Automotive Control Systems For Engine, Driveline, and Vehicle Second edition With 345 figures and 13 tables
Prof. Dr.-Ing. Uwe Kiencke Universität Karlsruhe (TH) Department of Electrical Engineering 76187 Karlsruhe Germany [email protected] Prof. Dr. Lars Nielsen Division of Vehicular Systems Department of Electrical Engineering Linköping University 581 83 Linköping Sweden [email protected]
Library of Congress Control Number: 2005922217 ISBN 3-540-23139-0 Springer Berlin Heidelberg New York This work is subject to copyright. All rights are reserved, whether the whole or part of the material is concerned, specifically the rights of translation, reprinting, reuse of illustrations, recitation, broadcasting, reproduction on microfilm or in other ways, and storage in data banks. Duplication of this publication or parts thereof is permitted only under the provisions of the German Copyright Law of September 9, 1965, in its current version, and permission for use must always be obtained from Springer-Verlag. Violations are liable to prosecution under German Copyright Law. Springer is a part of Springer Science+Business Media springeronline.com © Springer-Verlag Berlin Heidelberg 2005 Printed in Germany The use of general descriptive names, registered names, trademarks, etc. in this publication does not imply, even in the absence of a specific statement, that such names are exempt from the relevant protective laws and regulations and therefore free for general use. Typesetting: Data conversion by the author. Final processing by PTP-Berlin Protago-TEX-Production GmbH, Germany Cover-Design: Medionet AG, Berlin Printed on acid-free paper 62/3141/Yu – 5 4 3 2 1 0
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64
3. ENGINE MANAGEMENT SYSTEMS
between 2000 and 3000 rpm. For even lower resonant frequencies the geometric dimensions of the inlet pipes become too large. The frequency of air pulsation in the inlet pipe is n · CY L . (3.38) fp = 2 The factor 2 is due to the fact that air is aspirated only every second cycle in a four stroke process. For example, the pulsation frequency for a six cylinder engine (CY L = 6) at an engine speed of n = 6000 rpm is fp = 300 Hz. The air mass per cylinder can be calculated by integrating the mass air flow m ˙ a over one pulsation period. tb ˙ a dt (3.39) ma = m ta
The limits (begin ta and end tb ) of integration are given by tb − t a =
1 2 = fp n · CY L
,
(3.40)
and therefore, the aspirated air for one cylinder per cycle is 1
ma =
fp
m ˙ a dt .
(3.41)
0
The air supply ma can be calculated by integration of the mass air flow signal. The sampling rate must be high enough to avoid aliasing, and therefore it is about 5 − 10 times higher as the highest pulsation frequency. Eventual nonlinear characteristics of the air flow meter must be compensated for before the integration. A linear characteristic can be obtained by e.g. multiplying the sensor characteristic with it’s inverse. Thus an eventual bias introduced by the integration can be avoided [68]. The proper timing for integration (ta , tb ) can be derived from the crankshaft angle αcs signal. For example, if the crankshaft sensor has 60 teeth, the duration of tb − ta = f1p is equivalent to ∆αCS = 120◦ in a six cylinder engine. This is given by the shift of 20 teeth of the crankshaft sensor. Unfortunately, mass air flow is synchronized to time and not to the crankshaft angle αCS . Since mass air flow m ˙ a is not sampled at start and stop times ta and tb , it must be interpolated: * # t1 − ta t1 − t a +m ˙ a (t1 ) 1 − m ˙ a (ta ) = m ˙ a (t0 ) Ts Ts * # tn+1 − tb tn+1 − tb m ˙ a (tb ) = m ˙ a (tn ) +m ˙ a (tn+1 ) 1 − Ts Ts The integration is approximated e.g. by the trapezoidal rule: Ts t1 − ta ma ≈ (m ˙ a (ta ) + m ˙ a (t1 )) +m ˙ a (t1 ) + 2m ˙ a (t2 ) + · · · CY L Ts # * tn+1 − tb · · · + 2m ˙ a (tn−1 ) + m ˙ a (tn ) + (m ˙ a (tn ) + m ˙ a (tb )) 1 − Ts
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