Title: Honda. Push Belt. 2,44 - 0,41; 5,69. 91 Nm. 3-Zyl., 1,0 l
12004 International Continuously Variable and
Hybrid Transmission Congress September 23-25, 2004
Control and Operating Behavior ofContinuously
Variable Chain Transmissions
Roland Mölle
2- Ratio Control Design during Range Shifts in
Autarkic Hybrid
- Expanded Control Layout for Universal Use in
Chain Variator Applications
Presentation Outline
3Chain
Secondary Pulley
Primary Pulley
Hydro-Mechanical Torque Sensor
Introduction
4Typical CVT chain of amodern passenger carAudi
multitronicTorque Capacity up to 300 NmNominal
Power 162 kW (V6-3.0)
Pull type Chain in Audi/LuK CVT
5CVT Passenger Cars (worldwide, 2001)
6CVT Passenger Cars (worldwide, 2001)
7- Control Design for Range Shifts in Autarkic
Hybrid
- Expanded Control Layout for Universal Use in
Chain Variator Applications
Presentation Outline
8Main Advantage
Pressure
Transducer
Pulley 1
Disadvantages
- Torque information supplied by engine controller
Poor dynamics and limited accuracy - Need for high over clamping for security reasons
or additional measures - Oil flow always at maximum pressure level
Pulley 2
Directional
Control Valve
Constant Pressure
Oil Supply
Constant Pressure System
9Advantages
Torque
- Clamping pressures are automatically achieved
without superior control - High dynamically set clamping pressures due to
the pump function - Clamping pressure and speed ratio control
independent
Sensor
Pulley 1
Four Edges
Spool Valve
Line Pressure
Valve
Pulley 2
Actuator
Speed Ratio Control
Main Disadvantage
Constant Flow
Oil supply
- Permanent, constant oil flow required
HydraulicControl Unit
Pressure Differential
Valve
Constant Oil Flow System (PIV)
10Movable sensor plate
sF (axial movement of sensorplate)
Characteristics
- Torque sensor pressure proportional to torque
at the shaft
- Additional pump function at high torque
gradients
Conventional Torque Sensor(System PIV)
11Characteristic Curve of Actuator in Conventional
PIV Clamping Systems
400
40
p
p
Pcyl1
Pcyl2
CYL1
CYL2
p
p
pTorque
Pump
TORQUE
PUMP
bar
Nm
e
r
u
s
s
200
20
Torque
shift speed ds/dt
e
r
P
100
10
0
0
-1,5
-1
-0,5
0
0,5
1,5
mm
Slide valve travel
12- Control Design for Range Shifts in Autarkic
Hybrid
- Expanded Control Layout for Universal Use in
Chain Variator Applications
Presentation Outline
13The Autarkic Hybrid
- Opel Astra Caravan
- 60 kW Diesel engine
- 10 kW electric motor (120V)
- i2-CVT gearbox
Range shift in Autarkic Hybrid raised the need
for improved speed ratio control Extremely high
torque gradients during range shift(CVT engaged
vs. disengaged) Error signal lt0,002 required
Driveline of the Autarkic Hybrid
14Selection of control parameters
Absolute value of deviation
u
0
Algebraic sign of deviation
u
Variation of param. (gain scheduling)
Value of control variable
u
CVT Controller, Variable in Structure
15pAb
FAbpAb.Az
Az
FAnpAn.Az
Az
pAn
Influence of Disturbance Variables
16Problem Improved control system is needed for
speed ratio control at SYN (i0,458) during range
shift.
Solution Disturbance feedforward (torque)
Extension of the Speed Ratio Controller
17Extension of the Speed Ratio Controller
18The taken measures resulted in a significant
improvement of the quality of speed ratio control
and reliability of range shifts.
Apply same principles to the CVT controller for
universal use
- Regard to further disturbance variables
- Improved control over the whole spreading
range (improvements in quality, efficiency etc.) - Enable different control strategies ratio based
strategies (e.g. ground speed pto) vs. di/dt
control (passenger car / transportation work)
Results and further Aims
19- Control Design for Range Shifts in Autarkic
Hybrid
- Expanded Control Layout for Universal Use in
Chain Variator Applications
Presentation Outline
20- Main disturbance variables torque and speed ratio
lead to - Pulley Misalignment, shaft deflection, pulley
distortion, - change in clamping force ratio
Disturbance Variables
21setpoint
CVT
actualvalue
LinearController
Extension of the Control Structure
22Question Where to get the z-map from ?
Output of Linear Controller supposed to be Zero
in steady state!
setpoint
CVT
actualvalue
LinearController
Adaptation of z-map
23Adaptation of the sampling points Value of the
manipulated variable from linear controllerx
weighting factor.
- Weighting functions
- Gauss
- Cone
- ...
Adaptation Law
24START
Visualization and Discussion of the Adaptation
Process
25CVT in Drive Train Configuration
- Power demand leads to desired engine speed.
- New engine speed is achieved by changing the
CVTs speed ratio i. - Change in speed ratio di/dt affects the available
torque at the wheel T2!
- Controlling the rate of speed ratio change is
favorable
26Control of the Rate ofSpeed Ratio Change di/dt
Modification of the control structure
setpoint speed ratio
speed ratio
di/dt
CVT
27Control of the Rate ofSpeed Ratio Change di/dt
pdyn ds/dt / ( ACYLD )
- Axial pulley speedds/dt f ( di/dt, geometry )
- Damping coefficientD f ( speed )
ü 1/i
28Measured Results of the Control ofSpeed Ratio
Change ds/dt
29- Control Design for Range Shifts in Autarkic
Hybrid
- Expanded Control Layout for Universal Use in
Chain Variator Applications
Presentation Outline
30- Quality of speed ratio control was significantly
improved - The control structure was implemented using a
RCP- system running under Matlab/Simulink
(xPCTarget) and is currently running on a test
rig - For use in tractor applications it was also
implemented on a typical electronic control unit
(C167) both manually and using code generation
(dSpaceTargetLink 2.0) - Gathered z-maps can be used for different
purposes (scientific work, onboard diagnostic
purposes etc.) - Further optimization possible (improved di/dt,
z-max)
Summary
312004 International Continuously Variable and
Hybrid Transmission Congress September 23-25, 2004
Control and Operating Behavior ofContinuously
Variable Chain Transmissions
Roland Mölle
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