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le% A SAT **0
MILITARY TECHNICAL COLLEGE
CAIRO - EGYPT
MODELLING OF AN AIRCRAFT LONGITUDINAL CONTROL SYSTEM.
G. RABIE* **
A. KHATTAB A. ELZAHABY***
ABSTRACT
ThA papek deals with the modelling and 'imitation o6 an aikckait
Longitudinal control zyztem including a hyd4omechanicat boortek.
A bond gkaph model ob the boorte4 .ins developed. the equation's
dezckibing the boo4te4 ake deduced Pcom the bond gkaph taking into con-
'side/cation the bazic nontineakitiez. The motion ob aikcka6t iz kepke-
zented by a tkan46ek 6unction dezckibing itz behavioult du/Ling the .shoat
pekiod longitudinal owittation4. The validity (3,6 the deduced model
the boortek « 4tudied by the compalaton ob calculated tkanzient kezponze
o6 boo4te4 with cokkezponding expekimentat kezuttz. The ebiect o6 some
conztkuctionat and operational pakametekz on the dynamic behaviouk c(6 the
hyditautic boo4te4 and al4c4qt td Atudied by the exptoitation o6 the
deduced model.
INTRODUCTION
The study of aircraft stability during flight and the analysis of
the effect of different constructional and operational parameters of air-
craft and control system has been the subject of several studies. In
the case of aircraft with control systems equiped by hydromechanical servo-
units; this unit is usually represented by a simple linear model,[1] & [2].
Such simple models may be obtained by linearization of the equations
describing the unit or on the basis of experimental evaluation of behaviour
of the real units.
In this paper, the control system of an aircraft is the subject
of study. The system includes a hydromechanical servo unit; booster, supp-
lied by the hydraulic power from two different systems simultaniously (fig.1)
The pilot actuates the booster through alinear transmission system T1.
The booster; consequently displaces the elevator by means of another
Ass. Prof., Aeronautical Dept., M.T.C.
** Lecturer, Mech. Power Dept., M.T.C.
L2* Lecturer, Aeronautical Dept., M.T.C.
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SECOND A.S.A.T. CONFERENCE
21 - 23 April 1987 , CAIRO FM-3 368
P
transmission system T2.
In order to study the effect of the booster constructional and operational
parameters a bond graph model is developed. After assignment of the causality
the bond graph carries at the same time both the physical and mathematical
structure of the studied booster [3] & [4]. The equations describing the
booster could then be obtained systematically from the bond graph. The
simulation ,s realised on a digital computer by the exploitation of the ded-
uced model. The validity of the model is studied by comparing simulation
and experimental results.
The behaviour of aircraft longitudinal control is studied during the
short period longitudinal oscillation mode of flight. The developed model
allows to study the effect of the different constructional and operational
parameters of the booster.
MODEL OF AIRCRAFT
The equations describing the motion of aircraft during the short period
longitudinal oscillations are deduced assuming that: - The aircraft is a rigid body subjected to aerodynamic forces and
moments in addition to its weight.
- The gyroscopic effects, introduced by the presence of spinning rotors
are negligible.
- The center of gravity of aircraft is the origin of coordinate system.
- The horizontal steady flight is the reference flight regime.
- The aircraft velocity is not much affected during the short period
longitudinal oscillation.
During this mode of flight, the behaviour of aircraft is described by the
following transfer function; [5]:
do, di(s) = G/[sqcon2 + 2tshon + 1] (1)
The natural frequency and damping coefficient are functions of the aero-
dynamic parameters of aircraft. In order to evaluate these parameters; some
numerical values were found in the aircraft technical description books, others
were measured by limited experimental work of the aircraft in addition to the
exploitation of the data sheets.
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T2 H.Booster--." T1 A/c ilot
I H.Syst;2 I
Ixetrumente
H.Syst.1
SECOND A.S.A.T. CONFERENCE
21 - 23 April 1987 , CAIRO I
FM-3 1369
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Yig.1 Block scheme of aircraft loagitudiaal control system.
Fig.2 Hydraulic booster with one of the infinite-position D.C.V.disassembled. 1-Piston rod. 2-Connections for hyd.supply. 3-Two infinite-position directional control valves.
4-Hetura cnnnsctions.5-Twin piston cylinder. 5-Fixed disc.?-Flat rotary slide valve.
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I
FM-31370 SECOND A.S.T.CONFERENCE
21-23 April 1987 ,cairo
1
DESCRIPTION OF THE HYDRAULIC BOOSTER
The hydraulic booster used is a hydromechanical unit with a follow up
control system. The booster has two infinit-position directional control
valves with flat rotary-type slide valves. The two slide valves are inter-
connected within a common distributing assembly and operate in concert.
The actuating assembly is made up from a twin cylinder with two pistons
and one common piston rod (Fig.2 &3). Each directional control valve is
fed from a seperate hydraulic system to increase the reliability of the air-
craft control system. The booster is equiped with a feed back mechanism
( not shown in figures ) which brings the slide valve to the neutral position
when the piston rod reaches a final position corresponding to that of the
control rod.
BOND GRAPH OF THE HYDRAULIC BOOSTER
The hydraulic booster is supplied by the hydraulic power from two seperate
constant pressure systems, represented by two sources of effort SE1 and SE41
(fig.4). The four restrictions of each of the two directional control
valves are represented by the resdsteboes: Ra' Rb, Rc
and Rd, modulated by
the slider rotation angle 8, Each of the four resistances in the first valve
is commonly manufactured to be identical with the corresponding one in the
second valve. The elements SE9 and SE49 impose the constant return
pressures of both the power systems. The effect of fluid compressibility
in actuator cavities is represented by the capacitances Cl and C2 modulated
by the piston displacement; y. The resistances P. of bonds 21, 32 and 71
represent the resistance to internal leakage, while the resistance to external
leakage is represented by by the element Re of bonds 17 and 57. The
Transformation of hydraulic power to mechanical one and vice versa is insured
by four TF elements. The external load, depending on the deflection angle
of control surface is imposed by the source of effort SE27 modulated by the
piston displacement y. The resistance R25 represents the effect of friction
forces opposing the piston motion. The inertia of the moving parts is
taken into consideration by the inertia element 126.
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371 FM-3
SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
T
Psi
P52
e2ft Fig., Functional scheme of the hyd. booster.
9 18
Rb Ra -0-19" Q5 19 \
3T 51 3T
FIL—', 01--Al 8 i '-'" C 1 Re 2,./ Qb Q ON 9 P Qb .L_A R; st-L-44 0 45 OF—ErSE
iciit_, 0 12_,W -12: Psi-N.,79
r 13 r .2
tt —a.- Re Rd .17 P,3 0, 24, TF 131 A
RI 1---32 T Qi
133 PO 6 8 , 0 ATF
1 R q' 2," : A
431 4 145 of
/--A I 7o -46-711 ‹,0 9 —D. s.of r I 139
.1.i. N 014, P>-SE Q ----A R, SE 41- 34 0 Q 1 1-5-4-70 12-74 1 'r ' C,2 Re
t2 155 Ii pi Ns% v, ,— d t't 0
C 53
Flg.4 Augmented bond graph of the hyd.booster
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Ab
= Ad = rhg
Aa = A
c = 0
Ab
= Ad
0
Aa
= Ac
rh191 I
45 = bl - 0a1
Q13 = d1 - 0c1
Q17
= P5
I Re
Q18
= A.yo
Qil = (P5 -P13 1/B.
Q20 = Q5 - Q17 - Q18 Qi1 1
P51
(220'dt
Cl
= VI/B
SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
MATHEMATICAL MODEL OF THE HYDRAULIC BOOSTER
The equations
graph are as follows:
describing the hydraulic booster, deduced from the bond
Qa1 = Cd.Aa
1/
2( PS-PT) (2)
Qbl = Cd.AbI (3) 2(P
sl-P5)
c1 = C
d .A (4) /.2(P
sl-P
13)
0d1 = Cd.Ad (5) Y2(P
13-PT)'
Where the areas of valve orifices Aa, A
b, A
c & Ad are given, for the
small angular displacement of the slider, by;
for 9> 0 (6)
for 9< 0 (7)
(8)
(9)
(10)
(111
(12)
(13)
(14)
V 1 = V + A.y (15)
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SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
FM-3
T (16)
)24 = A.y
0 .="(P 45 -P13i )/R (17)
Q23 = Q24 Qi1 Qi - Q13 (18)
P 13
= 1 yr
Q .dt 6— 23
(19)
2
C2 = V2
/B V2
= V - A.y (20)
e35
= A.P5 (21)
e30
= A.P13
(22)
e29
= A.P45
(23)
e28
= A.P53
(24)
e27
= k .y (25)
e~5 = f
v.y• + F
c sign (y.) (26)
(27) e26 = - e35 - e20 - e29 e28 - 827 - e25
= 1
e26•dt (28)
I
The equations describing the lower part of the booster are similar
to these equations. They are also deduced in a similar way from the lower
half of the bond graph.
The hydraulic booster is equiped with a solid negative feed back mechanism,
for the small input displacement, characterizing the studied unit, the feed
back mchanism is described by;
0 = a1.z - a2.y (29)
MEASUREMENT OF THE HYDRAULIC BOOSTER TRANSIENT RESPONSE
The transient response of the hydraulic booster is evaluated experimentally
by the simultaneous measurement and plotting of the control rod and piston rod
displacements. The control rod is rapidly displaced by means of a double
acting electromagnetic solenoid of adjustable stroke, 2, (Fig.5 6 6).
The measurement is realised by means of two inductive displacement pick-
ups (3) 6 (4). The recording of the measured variables is carried out by
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SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
FM-3 374
means of a Hottinger system with multi channel hot pin plotter.
Both of the two directional control valves are fed from a hydraulic
generator of constant pressure. The hydraulic generator includes a variable
displacement piston pump driven by means of a high power electric servomotor
of adjustable speed. The pump input pressure is boosted by means of a
centrifugal pump driven electrically. Both of the main pump input and
output pressures can be measured and controlled.
A hydraulic accumulator is installed to smooth out the pressure pulsation
resulting from the pump flow pulsation. The experimental work is realized
in the laboratories of chair of aircrafts of the M.T.C. The measured res-
ponse of the booster, y(t), for several magnitudes of input displacement Z(t)
is given in figure 7.
718, 5 Model soliencef the experissabal arraagssiont fer the
asasuressat of booster brasiest response.
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SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
FM-3 375
Fig. 6. Test Stand
1 Hydraulic booster.
2 Electromagnetic Solenoid.
3 & 4..; Displacement inductive pick-ups.
Fig. 7 Records of measured transient response of booster.
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SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
FM-3 1376
VALIDITY OF THE HYDRAULIC BOOSTER MODEL.
The validity of the model of hydraulic booster is studied on the basis
of the comparison of simulation and experimental results. The simulation
is realized, by the exploitation of the equations describing the booster, on
a digital computer. Both the experimental and simulation results are given
in figure 8 for different magnitudes of input displacement.
The control rod is displaced by means of an electric solenoid. Sudden
step displacement of this rod was impossible due to its inertia, but it
reaches the required position within 15-20 ms,(Fig.8). For the simulation
the input displacement is represented during this period by a ramp.
A small damped oscillations in the'position of the control rod is observed
mostly due to the impact with the position limiter. These oscillations
were neglected during simulation The study of figure 8 shows acceptable
agreement between the simulation and experimental results. The linearity
of booster model is checked by calculating the response of booster to step
inputs of different magnitudes, the results are given in figure 9, from this
figure, one can conclude that the model presents -practically- a linear be-
haviour. A linear empirical model representing the booster in the design
conditions is deduced according to the method given by Schwarzenback [6).
The obtained model is a simple first order transfer function.
(301 Y/Z 1/ 1+0.0569s
Such a simple model can be applied for the modelling of aircraft con-
trol systems when the problems concerning the booster are not of interest
[1] & (2).
EFFECT OF INTERNAL LEAKAGE ON THE BOOSTER BEHAVIOUR.
The effect of internal leakage on the transient behaviour of hydraulic
booster is calculated for several values of resistance to internal leakage.
The calculation results are given in figure 10. The decrease of the
resistance to internal leakage introduces a considerable steady state error
regardless to its stabilizing effect, therefore a special attention should
be payed to check the state of inner seals. The permissible values of
internal leakage can be found taking into consideration both the permissible
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SECOND A.S.A.T.CONFERENM 21-23 April 1987 , CAIRO
7
______Input,z,exp.
Output,y,exp.
------lnput,z,a1m.
Outputa,sim.
0.5
0.1 U.c 004.
(a) z = 0.5 in
0.1 0.2 0.3 0.4
(b) Z = 1 Mm
0.
y
z - 2 as
z =0.5 in
0 00.1 0.4 0.3 e T
0.5
0.1 0.2 0.3 0.4 ■
(°)(c) z 1.5 an
$ Simulation and experimental result• of the hydraulic booster transient
reeponse avaluatioa,for different sagaitudos e# 1aput displammeat,z.
Fig. y step response of hyd.booeter
F18.10 Effect of the resistance to internal
for different amplitudes of
leakage On the transient response of
input displacement. hyd.booster.
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SECOND A.S.A.T.CONFERENCI 21-23 April 1987 , CAIRO
FM-3 378
error and the steady state requirements, mainly the required maximum booster
load. The effect of Bulk's modulus of fluid is also studied. The var-
iation of Bulk's modulus within its real range gave no significant effect on
the dynamic behaviour of the hydraulic booster.
SIMULATION OF AIRCRAFT LONGITUDINAL CONTROL SYSTEM.
The simulation of aircraft longitudinal control system, (Fig.1) is realized
by the exploitation of equations describing the aircraft and hydraulic booster.
The step response of the aircraft to a step displacement of control stick
is calculated for several values of resistance to internal leakage in the .
booster, The results are plotted in figure 11.
It is well seen that the iherease of internal leakage introduces a con-
siderable steady state error to the aircraft response.
0 0.5 1 1.5 (s) T
Fig.11 Effect of internal leakage in the booster
on the transient response of aircraft
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SECOND A,S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
IFM-31379
1
CONCLUSION ThiA papers death with the modelling and 'simulation o6 an aincitalit longi-
tudinal cont4ot system. A bond oaph model o6 the hyd4omecanicat hertvo-
unit; boo'ste'r; is developed. The equation's dehcnibing the booster we/Le
deduced pcom the bond oaph taking into conhidutation the baste nontineakitieh.
The aincuAt is frepkezented by the tnanz6e4 liunction deAutibing its behav-
iou4 &king the shoat peniod tongitudinat ohcittationh, The himutation 4:4
keatized on a digital computers by the exploitation o6 the equations deAc4ibing
the system. The vatidity o6 the model o6 boosters is studied - by compaking
himutation and expekimentat Itehutth. The compaitiAon shows that the deduced
model kep4ezent4 the /teat boosters behaviours with acceptable accuAacy.
This model a used to study the ebiect o6 intelmat leakage in the cylinders
on the t4anhient behaviours o6 the system. The 'simulation 'Emits proved
that the intettnat teakage,nega4dteAA o6 its e igect; intItoduceh a
steady state pozition eh404 to the 'response o6 hyd4autic boosters and ailtutalit.
LIST OF SYMBOLS al , a2 pakameteu o6 lieedback mechaniAm. (4ad/m)
A piston attea. (m2 )
Aa,Ab,Ac,Ad areas oA 4eAt4iction4o6 slide valve. tm2 I
B Bulk's modulus oA lituid. IN/m2)
cl , C2 capacitances. (m5 /N) Cd
diAchakge coeitiicient. (-I e27
loading 6o4ce. (Ni
e25'e26'e28'e30'e35 6o4ceh. (Ni
fv
' Vi4COUA Oiction coeWcient. (Nh/m)
Fc Static Oiction 6o4ce. (NI
G Gain oli ai4c/ta6t tuntlien 6unct4on. (-I
h Width o li spool valve 'sloth. (ml
1 inettia; 'reduced mash o6 all movable pants. (kg)
K loading coetgicient. (N/m)
Psi ,Ps2
'supply piteAAu/te. (pa) PT
4ettan pAe4Au4e. (pa) P5 , P13 , 45 pite44U4e4. (pal
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SECOND A.S.A.T.CONFERENCE 21-23 April 1987 , CAIRO
FM-31380
4al,S2 b1Xcl,Qdl Flow Aate4 through valve poAt4. (m3/4)
Qi . Qii . 4i2 internal leakage yow Aate4. (m3/4)
Qe1 Qe2 external leakage stow /tate& (m3/4) ' 0 4 '4 X X ,4 5' /7 18 20 23
24 Atow Aate4. (m3/4)
radius. (m)
Re Aeisiztance to external Leakage. (W4/m51 R .
5' Aezatance to telmat leakage. INA/m
Laplace openato4.
t,T time. (4ec.) v , vl , v2
volumes. (m3 )
piston displacement. (m)
control nod dizptacement. Im1
a angle o attack o6 aiAcAaAt. (rad.)
deAtection angle o6 control -tick. (Aad.)
deAtection angle o elevator. (had.)
9 notation angle ()A notary spool. (had.)
zpeciiic mace oA Atuid. Ihg/m3 1
0., natukat Auquency. (4ad/4)
damping coeAycient.
REFERENCES
11 ] David E. BISCHOFF, "The deAinition o6 short-peftiodAlying qualities
chaucteAittic4 via equivalent system", J. Ai4c4aAt, vot.20,No.6 June
1983,pp494-499.
(2 1 Donald T. BERRY et al, "In-Alight evaluation oA control system pure
time delays", J. AiAcita6t,Vol.19,N0.4,ApAil 1982,pp 318-323.
(3 ] Bernard ETKIN, "Dynamic's oA blight stability and control", J.W,NY.,1982
(.4 1 KARNOPP V., ROSENBERG R.C., " System dynamics, a uniAied approach",
Wiley Intmscience,1975.
1.5 1 VAN DIXHOORN J.J., "Bond graph and challenge oA auniyed modelling
theory oi physical systems", Simulation 80 conic., InteAtaken,Shweiz.,
June 1980.
(6 ] SCHWARZENBACK J. and GILL K.F., "System modelling and contnot",J.W,
NV,1978.