performance et comportement des vehicules · 2015-10-11 · 2.255 210@5300 210@3500 15.9 15.7 bmw...
TRANSCRIPT
Vehicle Performance
Pierre Duysinx Research Center in Sustainable Automotive
Technologies of University of Liege
Academic Year 2015-2016
1
Lesson 1: Power sources and Transmission
2
Outline
MOTORIZATION CHARACTERISTICS
Piston engines
Torque speed curves
Approximation of curves
Electric machines
POWER AND TRACTIVE FORCE AT WHEELS
Transmission efficiency
Gear ratio
Expression of power and forces at wheels
Power and forces diagram
3
References
T. Gillespie. « Fundamentals of vehicle Dynamics », 1992, Society of Automotive Engineers (SAE)
J.Y. Wong. « Theory of Ground Vehicles ». John Wiley & sons. 1993 (2nd edition) 2001 (3rd edition).
W.H. Hucho. « Aerodynamics of Road Vehicles ». 4th edition. SAE International. 1998.
M. Eshani, Y. Gao & A. Emadi. Modern Electric, Hybrid Electric and Fuel Cell Vehicles. Fundamentals, Theory and Design. 2nd Edition. CRC Press.
R. Bosch. « Automotive Handbook ». 5th edition. 2002. Society of Automotive Engineers (SAE)
4
Piston engines
5
4 stroke engines: gasoline
In 1862, Beau de Rochas developed a operation sequence that is still now the basis of any piston engine operations
The 4-stroke engine requires to 2 crankshaft revolutions to accomplish one thermodynamic cycles, which means 2 compression and expansion motions of the piston.
6
4 stroke engines: gasoline
Stroke 1: Fuel-air mixture introduced into cylinder through intake valve
Stroke 2: Fuel-air mixture compressed
Stroke 3: Combustion (roughly constant volume) occurs and product gases expand doing work
Stroke 4: Product gases pushed out of the cylinder through the exhaust valve
Compression
Stroke
Power
Stroke Exhaust
Stroke
A
I
R
Combustion
Products
Ignition
Intake
Stroke
FUEL
Fuel/Air
Mixture
7
4 stroke engines: diesel
The Four stroke Compression Ignition (CI) Engine is generally denoted as the Diesel engine
The cycle is similar to Otto cycle albeit that it requires a high compression ratio and a low dilution (air fuel) ratio.
Air is admitted in the chamber and then compressed. The temperature rises the ignition point and then the fuel is injected at high pressure. It can inflame spontaneously.
There is no need for a spark and so stoichiometric air fuel ration is not necessary.
8
4 stroke engines: diesel
Stroke 1: Air is introduced into cylinder through intake valve
Stroke 2: Air is compressed
Stroke 3: Combustion (roughly constant pressure) occurs and product gases expand doing work
Stroke 4: Product gases pushed out of the cylinder through the exhaust valve
Compression
Stroke
Power
Stroke
Exhaust
Stroke
A
I
R
Combustion
Products
Intake
Stroke
Air
Fuel Injector
9
2-stroke engines
Dugald Clerk has invented the 2-stroke engine in 1878 in order to increase the power to weight ratio for a equal volume.
The 2-stroke engines is also simpler with regards to valve system
The 2-stroke principle is applicable to both spark ignition engine and compression ignition engine. It is however more usual with spark ignition engines.
The 2-stroke engine involves two strokes and the cycle is carried out during one single crankshaft revolution.
10
2-stroke engines
Intake (“Scavenging”)
Compression Ignition
Exhaust Expansion
Fuel-air-oil
mixture
Fuel-air-oil
mixture
compressed
Crank
shaft
Check
valve
Exhaust
port
11
2-stroke engines
Stroke 1: Fuel-air mixture is introduced into the cylinder and is then compressed, combustion initiated at the end of the stroke
Stroke 2: Combustion products expand doing work and then exhausted
* Power delivered to the crankshaft on every revolution
12
Troque-speed curves of ICE engines
13
Torque speed curves of ICE
Suppose that the gas pressure is remaining constant along the power stroke, its work is given by:
The work of the n pistons over the cycle is:
For an k-stroke engine the duration of the cycle is given by
14
Torque speed curves of ICE
It comes the power curves with respect to rotation speed:
The torque speed curve is
w w 15
Indicated mean effective pressure
The indicated mean effective pressure imep is a fictitious constant pressure that would produce the same work per cycle if it acted on the piston during the power stroke
imep does not depend on engine speed, just like torque
imep is a better parameter than torque to compare engines for design and output because it is independent of engine speed, N, and engine size, Vd.
R
pp
R
di
d
Ri
d
i
n
UAimep
n
NVimepW
NV
nW
V
Wimep
2
Puisque alors imepcycleT W T
16
Brake mean effective pressure
The brake mean effective pressure (bmep) is defined similarly to the indicated mean effective pressure as a fictitious constant pressure that would produce the same brake work per cycle if it acted on the piston during the power stroke
2 C
2
b dR
d d R
W bmep VC nbmep
V V n
17
Brake and indicated mean effective pressure
Order of magnitude of the brake mean effective pressure of modern engines:
Four-stroke engines:
Atmospheric
SI engine: 850 – 1050 kPa
CI engine: 700 – 900 kPa
Turbocharged
SI engine: 1250 - 1700 kPa
CI engine: 1000 - 1200 kPa
Two-stroke engines
SI engine : idem 4 stroke
Large 2-stroke diesel engines (e.g. boat) ~1600 kPa
Remark
Bmep is maximum at maximum torque and wide open throttle
At nominal power, the bmep is lower by 10 to 15%
18
Brake and indicated mean effective pressure
Vehicle Engine
type
Displ.
(L)
Max Power
(HP@rpm)
Max Torque
(lb-ft@rpm)
BMEP at
Max BT
(bar)
BMEP at
Rated BP
(bar)
Mazda
Protégé LX
L4 1.839 122@6000 117@4000 10.8 9.9
Honda
Accord EX
L4 2.254 150@5700 152@4900 11.4 10.4
Mazda
Millenia S
L4
Turbo
2.255 210@5300 210@3500 15.9 15.7
BMW
328i
L6 2.793 190@5300 206@3950 12.6 11.5
Ferrari
F355 GTS
V8 3.496 375@8250 268@6000 13.1 11.6
Ferrari
456 GT
V12 5.474 436@6250 398@4500 12.4 11.4
Lamborghini
Diablo VT
V12 5.707 492@7000 427@5200 12.7 11.0
19
Piston engines characteristics
Good combustion properties (and so the maximum torque) are obtained for a medium (design) rotation speed.
For increasing rotation speed, the admission pressure drop and the engine frictions are increasing and the brake mean effective (and the torque) pressure is dropping.
Power = torque x speed is still increasing till the torque drops is so high than power is falling as well.
A low regimes, the dilution is high and the combustion is deteriorated, while heat transfer to piston and walls is becoming more important. It comes that the mean effective pressure and the torque is also reduced. 20
Piston engines characteristics
Gillespie, Fig. 2.1
21
Standard performances of ICE
Torque-curves provided by the manufacturer are giving the basic power of the engine
Basic power = performance with requirement equipment to insure the normal conditions: ventilator, water pump, oil pump, exhaust pie, air filter
Pay attention to the multiplication of accessories and auxiliary equipments (air conditioned, steering wheel assistance, braking systems, electric generator) reduce the power available at the wheels by a significant part.
22
Standard performances of ICE
SAE (Society of Automotive Engineers, USA): the power of the engine without its auxiliaries, with parameters adapted to each regimes (ignition advance, carburetor). Ideal maximum power.
DIN (Deutsche Industrie Normen) and CE. The engine has to provide the power necessary to operate all its needed auxiliaries while the parameters settings are the standard ones.
CUNA. Italian system that is in between DIN and CAE: no accessories but standard settings.
23
Power consumption of auxiliaries
The power consumption of the accessories is increasing and has a significant impact on the output power available for the propulsion especially for the small engines and the electric motors
24
Effect of atmospheric conditions
The atmospheric conditions (temperature, pressure, hygrometry) affects the engine performances.
Reference atmospheric conditions:
T°=15.5°C = 520°R = 60°F
p= 101.32 kPa = 14.7 psi = 76 cm Hg
Wong is referring to the correction formulae proposed by Taborek (1956):
Ba barometric pressure
T the temperature (in °R) at admission pipe
Bv vapour pressure to account for the effect of the humidity
25
Effect of atmospheric conditions
For SI engines (gasoline)
For CI engines (diesel) the effect of atmospheric pressures is more complex:
The atmospheric conditions may impact significantly tje engine performances (Wong Fig. 3.24)
00
0
( )a vB B TP P
B T
00
0
( )a vB B TP P
B T
26
Effect of atmospheric conditions
Norm EEC 80/1269 – ISO 1585 – JIS D 1001 – SAE J1349 for SI engines (gasoline)
Standards conditions (temperature T0= 298 K and dry air pressure p0= 99 kPa)
Corrected power
PP a0
298/)(
)(/99
6.02.1
KTB
kPapA
BA
p
PT
a
27
Effect of atmospheric conditions
Norm EEC 80/1269 – ISO 1585 – JIS D 1001 – SAE J1349 for CI engines (diesel)
Standards conditions (temperature T0= 298 K and dry air pressure p0= 99 kPa)
Corrected power
298/)(
)(/99
5.17.0
KTB
kPapA
BA
p
PT
a
PP a0
28
Curve fitting of ICE characteristics
Two families of curves
Fitting to a power function
Fitting of a polynomial
Data
Nominal (maximum) power
Maximum torque
r¶egimes. Par c
le P1 = Pmaxe !1 = !nom;
al C2 = Cmaxt !2 = !Cmax .
29
Power approximation
On look for a power function of the type
Data
That is
!1 = !nom P1 = Pmax!2 = !Cm ax
P2 = Cmax!Cm axd C
d!
¯¯!2
= 0
¯ ¯ ¯ ¯
P = P 1 ¡ A j ! ¡ ! 1 j b b > 0
A =
P 1 ¡ P 2
j ! 1 ¡ ! 2 j b
j ¡ j
b =
! 1
! 2
¡ 1
P 1
P 2
¡ 1
¯
30
Power approximation
Maximum power in P1: OK
Maximum torque in w2:
Given (maximum) torque w2 :
be de couple y passe par un max
P(!2) = P2 = Cmax !Cmaxd C
d!
¯¯!2
=d (P=!)d!
¯¯!2
= 0¯¯
¯¯
µere des deux condition
a =P1 ¡P2j!1 ¡ !2jb P = P1 ¡ (P1 ¡P2)
¯¯ !1 ¡ !!1 ¡ !2
¯¯b
31
Power approximation
Maximum torque in w2:
Derivative of the power
Leads to the condition
¯¯
¯¯
ximal en ! = !2. On a :
d C
d!
¯¯!2
=!2
dPd!
¯!2¡P2
!22= 0 P2 = !2
dPd!
¯¯!2
¯¯
iv¶ee de l'expression de la puissance, il vient :
dPd!
¯¯!2
= ¡a b j!1 ¡ !2jb¡1 sign(!1 ¡ !2) (¡1) = a b (!1 ¡ !2)b¡1
pu etre omis puisque !1 > !2. On obtient ¯
P2 = !2 a b (!1 ¡ !2)b¡1 = b !2P1 ¡P2!1 ¡ !2
32
Power approximation
Fitted exponent b
Fitted approximation
j ¡ j
b =
! 1
! 2
¡ 1
P 1
P 2
¡ 1
¯
P
P ¡
P
P 1
= 1 ¡
µ
1 ¡
P 2
P 1
¶ ¯ ¯ ¯ ¯ ¯
1 ¡ !
! 1
1 ¡ ! 2
! 1
¯ ¯ ¯ ¯ ¯
b
C = P = !
33
Power approximation
Example: Peugeot engine XV3 943 cm³
One gets
uver pour l'approximation de type puiss
b =
!1!2¡ 1
P1P2 ¡ 1
=2¡ 1
1; 5996¡ 1 = 1; 698
34
Power approximation
Example: Peugeot engine XV3 943 cm³
Inserting this value into the expression of the curvature coefficient A
Finally the expression of the power approximation of the power writes
35
Polynomial approximation
Polynomial approximation
Power
Torque
proximation peut s'¶ecrire de maniµe
P(!)=Pmax 'nX
i=0
ai (!=!nom)i
. Le couple moteur est donn¶e par
C(!)=C1 'nX
i=0
ai (!=!nom)i¡1
36
Polynomial approximation
Polynomial approximation of order 3
Identification of the coefficients
lynome du troisiµeme ordre (n=3).
P(!)=P1 = a0 + a1 (!=!1) + a2 (!=!1)2 + a3 (!=!1)3
rmettant de
e P(0) = 0 endre en compte l
ue P(!1) = Pmax.
d que P(0) = 0 et qu
a0 = 0
a1 + a2 + a3 = 1
que ce maximum vaut Cmax :
P(!2) = P2 = Cmax !Cmaxd C
d!
¯¯!2
= 0
¯¯
posons n2 = !2=!1, il vient :
a1 n2 + a2 n22 + a3 n
32 = P2=P1
a2 + 2 a3 n2 = 0
¯¯
imer ces deux
s n2 = !2=!1,
37
Polynomial approximation
Polynomial approximation of order 4
Identification of the coefficient
Same as polynomial of order 3 + new condition on the maximum power in w1:
iµeme degr¶e.
P(!)=P1 = a0 + a1 (!=!1) + a2 (!=!1)2 + a3 (!=!1)
3
+ a4 (!=!1)4
le en !1, soit :
a1 +2 a2 +3 a3 +4 a4 = 0
38
Polynomial approximation
Polynomial approximation of order 4
Value of the coefficients
iµeme degr¶e.
P(!)=P1 = a0 + a1 (!=!1) + a2 (!=!1)2 + a3 (!=!1)
3
+ a4 (!=!1)4
:
a1 + a2 + a3 + a4 = 1
a1 + 2 a2 + 3 a3 + 4 a4 = 0
a1 n2 + a2 n22 + a3 n
32 + a4 n
42 = P2=P1
a2 + 2 a3 n2 + 3 a4 n22 = 0
¯¯
imer ces deux
s n2 = !2=!1,
39
Example: 2.0 HDI PSA engine
40
Example: 2.0 HDI PSA engine
0 500 1000 1500 2000 2500 3000 3500 4000 4500 50000
1
2
3
4
5
6
7
8
9
10
x 104 Caractéristique moteur
Vitesse moteur [min-1]
Puis
sance m
ote
ur
[W]
Cubique
Type Puissance
41
Example: 2.0 HDI PSA engine
0 500 1000 1500 2000 2500 3000 3500 4000 4500 50000
50
100
150
200
250
300
350
Couple moteur
Vitesse moteur [min-1]
Couple
mote
ur
[N.m
]
Cubique
Type Puissance
42
Engine Universal Performance Map
Golverk (SAE 941928) showed the a response surface with quadratic terms can represent with a sufficient accuracy the engine map
be [gr/kWh] the BFSC
T [Nm], the brake torque
N [rpm], the engine rotation speed
ai: Empirical coefficients to be identified
43
Engine Universal Performance Map
44
Electric machines
45
Performance curves of electric machines
46
Power electronic and control of DC machines
Working principle of a chopper 47
Power electronic and control of AC machines
Working principle of an inverter 48
DC motor: series and separated excitation
DC series motor DC motor with separated excitation
49
AC motors: induction vs synchronous
AC induction motor AC synchronous motor 50
Traction motor characteristics
At low speed: constant torque
Voltage supply increases with rotation speed through electronic converter while flux is kept constant
At high speed: constant power
Motor voltage is kept constant while flux is weakened, reduced hyperbolically with the rotation speed
Base speed: transition speed from constant torque to constant power regime
51
Traction motor characteristics
Independently from the motor technology, the global performance of the combined motor and its power electronic system offer three regimes
In low regimes, the current is limited and the torque is kept constant
Then, power becomes constant, which means that maximum torque as to reduced as P/N
At very high speed: the max power regime can not be maintained and power drops. Generaly this part is not considered in the EV design.
52
Traction motor characteristics
Speed ratio x = ratio between maximum rotation speed to base speed X ~ 2 Permanent Magnet motors
X ~ 4 Induction motors
X ~ 6 Switched Reluctance motors
For a given power, a long constant power region (large x) gives rise to an important constant torque, and so high vehicle acceleration and gradeability. Thus the transmission can be simplified.
53
Traction motor characteristics
Traction electric motor are able to sustain overcharging during a short period of time, typically 1 to 2 minutes.
Overcharging factor depends of the electric motor technology but can range from 2 to 4.
Thus one distinguishes the continuous power from the peak power (which is much higher)
One can admit as a basic approximation that both regimes can be deduced from each other by just a scaling factor
54
Traction motor characteristics
Electric machine efficiencies to transform the electric power to mechanical power is dependent on the working conditions
It can mapped on the torque/speed or power speed space
The efficiency mapping can be different when working as a motor (generally lower) than as a generator (often better)
55
Propulsion system architecture
56
Propulsion system
Gillespie, Fig 2.3 57
Layout of transmission
Transversal mounting Longitudinal mounting 58
Friction Clutch
Clutch in closed position Clutch in open position
59
Hydraulic coupling
Principle: use hydro kinetic energy of the fluid to transfer smoothly the power from the source to the load while amplifying the output torque
The input wheel plays the role of a pump whereas the output wheel acts as a turbine
One may add a fixed wheel (stator) to improve the efficiency
60
Friction and hydraulic clutches
Clutch efficiency
Friction clutch h=1
Hydraulic coupler: h~0.9
61
Manual gear boxes
Gear box principles
Input shaft
Output shaft
Intermediate shaft
Direct transmission
62
Manual gear boxes
63
Manual gear boxes
Neutral
1st 2nd
3rd
Reverse 64
Manual gear boxes
Gear selection 65
Manual gear boxes
Gear selection And selection mechanism
66
Power and tractive efforts at wheels
67
Power and tractive efforts at wheels
Manual gearbox efficiency:
Efficiency of a pair of gear (good quality) h= 99% à 98.5 %
Gear box: double gear pairs: h = 97.5%
Gear box: direct drive: h = 100%
Differential efficiency:
Longitudinal engine layout: axis offset and change of direction with hypoid gears: h = 97,5 %
Transverse engine layout (no change of direction): regular gears : h = 98,75%
68
Automatic gear boxes
The basic element of automatic gear boxes is the planetary gear train
Sun = planétaire Planet = satellite Annulus = Couronne 69
Planetary gear pair
Kinematics: Willys formula
Relation between the rotation speed of the different gear trains and the ratio of teeth of the sun and the annulus
Static: Equilibrium of torques
wCwCwPS
wSwP
C
P
Zi
Z
( )C C P P PS C PZ Z Z Zw w w
1(1 )PS P C
iT i T T
i
(1 )P C PSi iw w w
70
Automatic gear box
Principle of an automatic gear box based on double planetary gear trains
Mèmetaux Fig 5.9 71
CVT : Van Doorne System
Pulleys with variable radii
72
CVT : Van Doorne System
Working principle
By modifying the distance between the two conical half shells, one modifies the effective radii of the pulleys and so the reduction ratio
Originally the system was based on the centrifugal forces, but nowadays the system is actuated by depression engines and controlled by microprocessors
PERFORMANCES
Variable reduction ratios varying between 4 to 6 are achieved
Variable efficiency variable with the input torque and the rotation speed
73
Differential system
During turn, the inner and outer wheels have different rotation speeds because of different radii.
Differential systems allow a different speed in left / right wheels while one single input torque
Differential systems can be studied as planetary gears with equal number of teeth for sun and annulus.
Input shaft (engine)
Output shafts (wheels)
74
Differential system
Working principle of differential system 75
Differential system
Efficiency of differential
Longitudinal layout: 90 change of direction (bevel pair) + offset of the shaft (hypoïd gear): h = 97,5 %
Transversal layout: no bevel good quality gear pair: h = 98,75%
76
Transfer box
Special differential system for 4-wheel drive vehicle
The transfer box splits the torque between the front and rear axles.
77