Patent Publication Number: US-8983749-B1

Title: Road friction estimation system and method

Description:
FIELD OF THE INVENTION 
     The invention relates generally to tire monitoring systems for collecting measured tire parameter data during vehicle operation and, more particularly, to a system and method for estimating road friction estimation based upon such measurements. 
     BACKGROUND OF THE INVENTION 
     Vehicle-mounted tires may be monitored by tire pressure monitoring systems (TPMS) which measure tire parameters such as pressure and temperature during vehicle operation. Data from TPMS tire-equipped systems is used to ascertain the status of a tire based on measured tire parameters and alert the driver of conditions, such as low tire pressure or leakage, which may require remedial maintenance. Sensors within each tire are either installed at a pre-cure stage of tire manufacture or in a post-cure assembly to the tire. 
     Other factors such as the condition of the road surface including the road friction coefficient is an important considerations for vehicle operation and safety. It is accordingly further desirable to measure road friction and communicate road friction information to a vehicle operator and/or vehicle systems such as braking and stability. 
     SUMMARY OF THE INVENTION 
     According to an aspect of the invention a road friction coefficient estimation system and method is provided for calculating a road friction coefficient estimation. In a vehicle having a plurality of supporting tires, tire load estimation sensors are attached for estimating a dynamic load estimation on each of the plurality of tires. Tire slip angle calculation is conducted utilizing load estimation sensor data, whereby a dynamic slip angle estimation on each of the plurality of tires is made. From vehicle CAN bus sensors, vehicle acceleration and yaw rate operational parameters are obtained and a dynamic observer model calculates lateral and longitudinal force estimates on each of the plurality of tires. A load transfer ratio is estimated from the estimated dynamic load on each of the plurality of tires; and an individual wheel force estimation is calculated on each of the plurality of tires from the lateral and longitudinal force estimates on each of the plurality of tires. From the dynamic slip angle estimation on each of the plurality of tires and the individual wheel force estimation on each of the plurality of tires, a model-based friction estimation is made. 
     In another aspect, the friction estimation is conducted in real time based upon the tire sensor-obtained variables of slip angle and tire load and observer-derived estimations of forces on each of the plurality of tires. 
     In a further aspect, the dynamic observer model comprises a single-track, three degree-of-freedom model; the road friction coefficient estimation is made following a four-wheel vehicle model; and the road friction coefficient estimation is made utilizing a Brush-tire model. 
     DEFINITIONS 
     “ANN” or “Artificial Neural Network” is an adaptive tool for non-linear statistical data modeling that changes its structure based on external or internal information that flows through a network during a learning phase. ANN neural networks are non-linear statistical data modeling tools used to model complex relationships between inputs and outputs or to find patterns in data. 
     “Aspect ratio” of the tire means the ratio of its section height (SH) to its section width (SW) multiplied by 100 percent for expression as a percentage. 
     “Asymmetric tread” means a tread that has a tread pattern not symmetrical about the center plane or equatorial plane EP of the tire. 
     “Axial” and “axially” means lines or directions that are parallel to the axis of rotation of the tire. 
     “Brush model” means a one-dimensional quasi-static mechanical analog system used for analysis of rolling resistance. In the Brush model, the contact patch is divided into two sections: a forward static region where the tire tread adheres to the road surface, and an aft slide region where sliding occurs between tire and road. 
     “CAN bus” is an abbreviation for controller area network. 
     “Chafer” is a narrow strip of material placed around the outside of a tire bead to protect the cord plies from wearing and cutting against the rim and distribute the flexing above the rim. 
     “Circumferential” means lines or directions extending along the perimeter of the surface of the annular tread perpendicular to the axial direction. 
     “Equatorial Centerplane (CP)” means the plane perpendicular to the tire&#39;s axis of rotation and passing through the center of the tread. 
     “Footprint” means the contact patch or area of contact created by the tire tread with a flat surface as the tire rotates or rolls. 
     “Groove” means an elongated void area in a tire wall that may extend circumferentially or laterally about the tire wall. The “groove width” is equal to its average width over its length. A grooves is sized to accommodate an air tube as described. 
     “Inboard side” means the side of the tire nearest the vehicle when the tire is mounted on a wheel and the wheel is mounted on the vehicle. 
     “Lateral” means an axial direction. 
     “Lateral edges” means a line tangent to the axially outermost tread contact patch or footprint as measured under normal load and tire inflation, the lines being parallel to the equatorial centerplane. 
     “Net contact area” means the total area of ground contacting tread elements between the lateral edges around the entire circumference of the tread divided by the gross area of the entire tread between the lateral edges. 
     “Non-directional tread” means a tread that has no preferred direction of forward travel and is not required to be positioned on a vehicle in a specific wheel position or positions to ensure that the tread pattern is aligned with the preferred direction of travel. Conversely, a directional tread pattern has a preferred direction of travel requiring specific wheel positioning. 
     “Outboard side” means the side of the tire farthest away from the vehicle when the tire is mounted on a wheel and the wheel is mounted on the vehicle. 
     “Peristaltic” means operating by means of wave-like contractions that propel contained matter, such as air, along tubular pathways. 
     “Piezoelectric Film Sensor” a device in the form of a film body that uses the piezoelectric effect actuated by a bending of the film body to measure pressure, acceleration, strain or force by converting them to an electrical charge. 
     “Radial” and “radially” means directions radially toward or away from the axis of rotation of the tire. 
     “Rib” means a circumferentially extending strip of rubber on the tread which is defined by at least one circumferential groove and either a second such groove or a lateral edge, the strip being laterally undivided by full-depth grooves. 
     “Sipe” means small slots molded into the tread elements of the tire that subdivide the tread surface and improve traction, sipes are generally narrow in width and close in the tires footprint as opposed to grooves that remain open in the tire&#39;s footprint. 
     “Slip Angle” is the angle between a vehicle&#39;s direction of ravel and the direction in which the front wheels are pointing. Slip angle is a measurement of the deviation between the plane of tire rotation and the direction of travel of a tire. 
     “Tread element” or “traction element” means a rib or a block element defined by having a shape adjacent grooves. 
     “Tread Arc Width” means the arc length of the tread as measured between the lateral edges of the tread. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention will be described by way of example and with reference to the accompanying drawings in which: 
         FIG. 1  is a block level diagram of the system employed in the estimation of slip angle and load on a vehicle&#39;s tires. 
         FIG. 2  is a block level diagram of the system for using tire load and slip angle of  FIG. 1  with the vehicle CAN Bus parameters in the estimation of wheel force and coefficient of friction. 
         FIG. 3A  is a graph of steering angle over time used in conducting system verification. 
         FIG. 3B  is a graph of lateral displacement [m] vs. longitudinal displacement [m] along a vehicle experimental path. 
         FIG. 4A  is a graph of lateral force F y  on the rear right tire over the path showing actual force and estimated. 
         FIG. 4B  is a graph of lateral force F y  on the rear left tire over the path showing actual vs. estimated comparative results. 
         FIGS. 5A and 5B  are graphs showing lateral force estimated vs. actual for the front right and front left tires, respectively. 
         FIG. 6A  is a graph showing steering angle over time for the experimental vehicle path. 
         FIG. 6B  is a graph of longitudinal displacement [m] vs. lateral displacement [m] over the experimental vehicle path. 
         FIGS. 7A and 7B  are graphs showing lateral force estimated vs. actual for the right and left rear tires, respectively. 
         FIGS. 8A and 8B  are graphs showing lateral force estimated vs. actual for the right and left front tires, respectively. 
         FIG. 9  is a graph of an experimental vehicle path showing y and x vehicle position coordinates. 
         FIGS. 10A and 10B  are graphs showing lateral tire force actual (Force Hub) vs. Estimated (Observer) comparative results. 
         FIG. 11  is a Gough-plot using brush tire model. 
         FIG. 12  is a graph of the brush tire model showing tire lateral force vs. slip angle for three coefficient of friction values: 1, 0.6, 0.2 at a normal loading F z  of 4000 N. 
         FIG. 13  is a force diagram for a four wheeled vehicle. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     Referring first to  FIG. 1 , a strain sensor system and method of estimating a tire load and a tire slip angle is shown in a block level diagram. The load on a vehicle tire may be estimated by a tire based sensor system employing one or, preferably, a pair of strain or bending sensors  14  mounted to a tire at opposite sidewall locations  30 . The strain sensors react to the sidewall deflections of the tire and, in measuring the extent of deflection, provide a basis for estimating both load and slip angle of the tire. A signal  16  from each of the bending sensors  14  is transmitted to a signal processor as will be explained. In addition, a tire pressure monitoring system  18  is mounted to the tire and functions to measure and transmit tire pressure data  20  to the signal processing unit. The tire sidewall strain sensor signal(s) are used in parallel signal processing paths; a first path which uses the signal (s)  16  to estimate tire load, indicated by path  22 . The second processing path, indicated at numeral  24 , uses the sidewall deflection information to estimate slip angle. Co-pending U.S. patent application Ser. No. 13/609,695, filed Sep. 11, 2012, entitled “TIRE SIDEWALL LOAD ESTIMATION SYSTEM AND METHOD”, teaches the methodology and system of path  22  and is incorporated herein in its entirety by reference. The system is used on a vehicle equipped with tires of conventional construction, having a tread component at a tire crown region which contacts a ground surface during rolling operation. The tire mounts to a rim in conventional manner. The sensors are preferably piezoelectric bending sensors, or other suitable strain sensors commercially available, of a type operational to bend and reconfigure when subjected to a bending force and thereupon generate an electrical signal indicative of the magnitude of bending reconfiguration in the sensor body. The bending signals are thus indicative of the magnitude of the bending strain within the sidewall to which the sensor is attached. When the bending force is removed, the sensor resumes its original configuration. By way of example, without intent to limit the scope of the invention, a piezoelectric bending sensor such as bending film sensor commercially offered by Measurement Specialties, Inc. located at 1000 Lucas Way, Hampton, Va. 23666 may be employed. 
     In addition, the lateral sidewall deflection of the tire is analyzed for the purpose of estimating the slip angle of the tire as indicated by the vertical block path  24 . “Slip Angle” is the angle between a vehicle&#39;s direction of ravel and the direction in which the front wheels are pointing. Slip angle is a measurement of the deviation between the plane of tire rotation and the direction of travel of a tire. The slip angle of a moving vehicle tire is useful information in vehicle control and stability systems. As braking and other control systems in vehicles become more interrelated, an estimation of tire slip angle is useful in stability and control system such as anti-locking brakes. A slip angle estimation system is taught and disclosed by co-pending U.S. Patent Application Ser. No. 61/734,526 filed Dec. 7, 2012, entitled “Tire Slip Angle Estimation System and Method”, likewise incorporated herein in its entirety by reference. The sensor signal(s) are analyzed by finding the signal peak, extracting the linear portion of the curve, and fitting a line to the extracted curve in a least squares sense. An estimate of the difference in the signal slope provides a basis for concluding the slip angle present in the tire. The signal processing represented by sequential steps of processes  22 ,  24  result in an estimation of tire load  26  and  28  on a continual basis as the tire is in use. Each tire is analyzed in respective application of processes  22 ,  24  to generate the load and slip angle for each using sidewall deflection information. 
     In addition to the sensor signals from the inner and outer sidewall sensors, inflation pressure is measured by a tire pressure monitoring system (TPMS) mounted to the tire, of a type commercially available. The TPMS system includes a pressure sensor that mounts to a tire in communication with an internal tire air cavity and functions to measure the air pressure within the tire cavity and transmit the measured pressure data to a receiver. The measurement of the TPMS may further include a temperature sensor that measures tire temperature. Measured pressure value is transmitted by the TPMS system for inclusion in the load and slip angle estimations  22 ,  24 . 
     Pursuant to the invention, a modeling procedure is adopted utilizing the load and slip angle estimation of  FIG. 1  in the coefficient of friction estimation system and methodology represented in block diagram form by  FIG. 2 . The modeling procedure adopted is summarized in the following table. 
     
       
         
           
               
               
               
               
             
               
                 TABLE 1 
               
               
                   
               
               
                 S.  
                   
                 Modeling  
                   
               
               
                 No 
                 System 
                 Procedure Adopted 
                 System Output 
               
               
                   
               
             
            
               
                 1 
                 Vehicle 
                 8-DOF non-linear  
                 a Y , a X , r 
               
               
                   
                   
                 vehicle model 
                   
               
               
                 2 
                 Tire model + Intelligent  
                 Combined-slip tire 
                 F Z  , α 
               
               
                   
                 tire emulator 
                 model-Magic Formula  
                   
               
               
                   
                   
                 and Dugoff tire models 
                   
               
               
                 3 
                 Driver model 
                 Single-point preview  
                 δ 
               
               
                   
                   
                 driver model 
                   
               
               
                 4 
                 Observer 
                 Sliding mode observer 
                 
                   
                 
               
               
                   
                   
                 (SMC)-Single-track 
                   
               
               
                   
                   
                 3-DOF model based 
                   
               
               
                 5 
                 Individual wheel  
                 Four-wheel vehicle 
                 
                   
                 
               
               
                   
                 force estimation 
                 model 
                 
                   
                 
               
               
                 6 
                 Friction estimation  
                 Artificial neural  
                 μ estimated   
               
               
                   
                 algorithm 
                 network (ANN) based 
               
               
                   
               
               
                 a Y : Lateral acceleration 
               
               
                 a X : Longitudinal acceleration 
               
               
                 r: Yaw rate 
               
               
                 F Z  : Tire normal load 
               
               
                 α: Tire slipangle 
               
               
                    : Total lateral force on the front tires 
               
               
                    : Total lateral force on the rear tires 
               
               
                    : Total longitudinal force on the front tires 
               
               
                    : Individual wheel forces 
               
               
                 μ estimated : Estimated tire-road friction coefficient 
               
            
           
         
       
     
     Using the above modeling procedure, the functional block diagram of  FIG. 2  demonstrates coefficient of friction estimation in an exemplary four-wheeled vehicle  34 . The system may be adapted to vehicles having more or fewer wheel assemblies if desired. The vehicle  34  is equipped with four tire/wheel assemblies  12 . Vehicle based sensors are employed for the purpose of providing by means of vehicle CAN Bus  36  lateral and longitudinal acceleration data a x , a y ; and yaw rate “r” in a single point preview driver model output δ. An observer  38  receives as input CAN Bus acceleration data a x , a y ; and yaw rate “r” data. The observer  38  is a sliding mode observer (SMC)-Single-track 3 degree of freedom (DOF) model. From the CAN-Bus data, the observer  38  functions to output total lateral force on the front and rear tires and total longitudinal force on the front tires for estimation of individual wheel force  40 , using a four-wheel vehicle model as shown in  FIG. 13 . 
     The model may be implemented using any conventional commercial mathematical simulation tool such as, but not limited to Simulink commercially available from The Mathworks, Inc. located at 3 Apple Hill Drive, Natick, Mass. 01760. Simulink® is a block diagram environment for multi-domain simulation and model based design. It supports system-level design, simulation, automatic code generation, and continuous test and verification of embedded systems. Simulink provides a graphical editor, customizable block libraries, and solvers for modeling and simulating dynamic systems. It is integrated with MATLAB®, enabling a user to incorporate MATLAB algorithms into models and export simulation results to MATLAB for further analysis. 
     From the observer generated lateral and longitudinal force estimations, individual wheel force estimations (block  40 ) are made using the above four-wheel vehicle model. The individual wheel force estimation outputs are applied to the friction estimation algorithm (Brush-tire model based) as shown by block  42 , resulting in an estimation of road surface coefficient of friction  44 . The “Brush Tire Model” represents a one-dimensional quasi-static mechanical analog system used for analysis of rolling resistance. In the Brush model, the contact patch is divided into two sections: a forward static region where the tire tread adheres to the road surface, and an aft slide region where sliding occurs between tire and road. 
     The observer performance and analytical results were validated experimentally for two extreme cornering maneuvers: 
     1. Double lane change (on high-mu conditions) and 
     2. Fish hook maneuver (on low-mu surface conditions). 
     The observer Gains: 
     K1=100 
     K2=1000000 
     K3=10 
     K4=10000 
     K5=100 
     K6=100000 
     The observer gains were optimized using an iterative process.  FIG. 3A  shows a graph of the steering angle vs. time in the double lane change maneuver on a road surface having a high mu condition of 0.8.  FIG. 3B  shows a vehicle path graphing longitudinal displacement [m] vs. lateral displacement [m]. Estimation results are represented by  FIGS. 4A ,  4 B,  5 A, and  5 B graphing F y  [N] vs. time for the rear right, rear left, front right, and front left tires, respectively, for the double lane change maneuver (1). The close correlation between the actual and estimated force values validates the accuracy of the estimation approach. 
     Referring to  FIGS. 6A ,  6 B experimental results are shown for the second extreme cornering maneuver, that of a fish hook. In  FIG. 6A , with a road surface condition of low mu (approx. 0.2) the steering angle [Deg] is graphed over time. In  FIG. 6B , the vehicle path is graphed as longitudinal displacement vs. lateral displacement [m] and approximates the shape of a fishhook. Estimation results are represented by  FIGS. 7A ,  7 B,  8 A and  8 B graphing F y  [N] vs. time for the rear right, rear left, front right, and front left tires, respectively, for the fishhook path of maneuver (2). As with the lane change path, the close correlation between the actual and estimated force values validates the accuracy of the subject observer estimation approach. 
     In  FIG. 9 , observer performance and experimental results are analyzed for a closed loop (y vs. x position) vehicle path followed by an experimental vehicle instrumented with an IMU (Inertial Measurement Unit) and force hubs of a type commercially available. An IMU is typically equipped to combine 3-axis accelerometers, 3-axis gyros, and/or 3-axis magnetic sensors for computing and outputting in real-time drift free three dimensional vehicle orientations that are continuous over a complete 360 degrees of motion. From the IMU, measurements of acceleration a x , a y , and yaw rate “r” are provided from the vehicle CAN Bus and inputted into the observer. The observer is set for the purpose of the conducted experiment to have Observer Gains of K1=5, K2=500, K3=50, K4=50, K5=1200 and K6=1000.  FIG. 10A  shows estimation results vs. actual [obtained from a force hub] for lateral tire force front;  FIG. 10B  for lateral tire force rear. The close correlation between estimated and actual results again confirms the validity of the subject observer-based estimation system and methodology. 
     Once the vehicle CAN Bus information is used to make an estimate of the tire lateral and longitudinal forces (F x , F y ) using the dynamic observer  38  ( FIG. 2 ), a sensor fusion approach is used. The sensor fusion approach combines the intelligent tire and vehicle information of tire load provided by the tire based TPMS unit  18  and the strain sensors  14  with the CAN bus information (a x , a y , and yaw rate “r”) to estimate the individual wheel forces (using the Four-wheel Vehicle Model). A road friction estimation algorithm then utilizes the individual wheel forces and slip angle estimation to estimate the road surface coefficient of friction as explained below. 
     The friction estimation algorithm utilizes the F x , F y , and F z  (longitudinal, lateral, and normal) load estimations applied to the Brush tire model. 
       FIG. 11  represents a Gough-plot using the Brush Tire Model. The ratio of Fy/Fz is plotted against the ratio −M z /F z Lines of constant friction coefficient (solid), constant side slip angle (dotted) and constant pneumatic trail (dash-dotted) are shown in the diagram of  FIG. 11 . It will be noted that a pair of values (F y , M y ) are uniquely defined for each F y /F z  coordinate for the model (1) above. 
     The following statements apply to the Brush Tire Model analysis: 
                     F   y     =     {               3   *   μ   *     F   z     *       tan   ⁢           ⁢     (   α   )         tan   ⁢           ⁢     (     α   sliding     )         *     (     1   -            tan   ⁢           ⁢     (   α   )         tan   ⁢           ⁢     (     α   sliding     )              +       1   3     *           tan   ⁢             2     ⁢     (   α   )           tan   2     ⁡     (     α   sliding     )             )                 for   ⁢           ⁢        α          ≤          α   sliding                           μ   *   F   *   sign   ⁢           ⁢     (   α   )                 for   ⁢           ⁢        α          &gt;          α   sliding                       ⁢     
     ⁢   Where   ⁢           ⁢     μ   ←       =     μ   =       2   *     C   py     *     a   2     *   tan   ⁢           ⁢     (     α   sliding     )         3   ⁢           ⁢     F   z                       (   1   )               
Substitute express for tan(αsliding) to eq (1) to get:
 
     
       
         
           
             
               
                 
                   
                     
                       ( 
                       
                         27 
                         * 
                         
                           μ 
                           2 
                         
                         * 
                         
                           F 
                           z 
                           2 
                         
                       
                       ) 
                     
                     - 
                     
                       ( 
                       
                         
                           18 
                           * 
                           μ 
                           * 
                           
                             F 
                             z 
                           
                           * 
                           tan 
                           ⁢ 
                           
                               
                           
                           ⁢ 
                           α 
                           * 
                           
                             C 
                             py 
                           
                           * 
                           
                             a 
                             2 
                           
                         
                         
                           1 
                           - 
                           
                             ( 
                             
                               Fy 
                               
                                 2 
                                 * 
                                 
                                   C 
                                   py 
                                 
                                 * 
                                 
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                                   2 
                                 
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                                 tan 
                                 ⁢ 
                                 
                                     
                                 
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                                   ( 
                                   α 
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                     + 
                     
                       ( 
                       
                         
                           4 
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                           * 
                           
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                             4 
                           
                         
                         
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                                   2 
                                 
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                                   ( 
                                   α 
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                   = 
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     The side force and self aligning torque are two linearly independent functions of side slip angle and friction coefficient, provided the tire is partially sliding. An estimate of friction can therefore be made as soon as the tire is partially sliding. 
       FIG. 12  represents a graph of tire lateral force [N] vs. slip angle [degrees] for three co-efficient of friction mu values of 1, 0.06, and 0.2. It will be appreciated that by determining lateral force vs. slip angle, an estimation of coefficient of friction can be made by solving equations (2) above for μ. 
     Friction coefficient estimation results are presented in the table below for three slip angle conditions. From the results, it is shown that the slip angle, normal force, and lateral force values define a unique estimation of friction coefficient for both low and high friction surfaces. 
     
       
         
           
               
               
               
               
               
             
               
                 TABLE 2 
               
               
                   
               
               
                 Slip  
                 Friction  
                 Normal  
                 Lateral  
                 Friction 
               
               
                 Angle (α) 
                 Surface 
                 Force [N] 
                 Force [N] 
                 Co-efficient 
               
               
                   
               
             
            
               
                   
               
            
           
           
               
               
               
               
               
            
               
                 α = 1.5 
                 Low 
                 4000 
                 770 
                 μ = 0.21 
               
               
                 α = 1.5 
                 High 
                 4000 
                 1700 
                 μ = 0.83 
               
               
                 α = 2.5 
                 Low 
                 4500 
                 990 
                 μ = 0.24 
               
               
                 α = 2.5 
                 High 
                 4500 
                 2600 
                 μ = 0.805 
               
               
                 α = 4 
                 Low 
                 5000 
                 1015 
                 μ = 0.22 
               
               
                 α = 4 
                 High 
                 5000 
                 6950 
                 μ = 0.81 
               
               
                   
               
            
           
         
       
     
     From the foregoing, it will be appreciated that the subject system and method of estimating a road coefficient of friction utilizes direct measurement of tire variables using wireless sensors  14  embedded inside the tire. Existing control systems have limited information regarding tire deformations, traction forces and road surface conditions. By implementing an “intelligent” tire technology, elimination of vehicle sensors may be possible as tire-based sensors provide accurate, reliable and real-time information about the magnitudes, directions, and limits of forces for each tire. In addition, accurate and real-time estimation of tire variables may be used to avoid tire saturation during an emergency maneuver. Early warning systems can benefit from these estimations to inform drivers about diminishing road traction abilities when the vehicle hits a slippery road surface or when the driver makes excessive steering. The information produced using the subject system and method, namely the magnitudes, directions, and limits of forces for each tire and estimation of road coefficient of friction, can be used in a predictive control framework in order to design more reliable lateral and longitudinal control systems for active systems. 
     Techniques proposed heretofore for the tire slip angle, force and friction coefficient estimations prior to the subject invention, depend chiefly on the vehicle sensors such as engine torque sensor, throttle position sensor, steering angle sensor, wheel speed sensor, yaw rate sensor, GPS receiver, strain gauges, steering torque, etc. The type and number of sensors used change according to the vehicle. The indirect techniques used in the existing control systems are generally known as “observer based techniques”, since the tire slip angle and traction force observers are designed based on the vehicle models and the measured vehicle states. The main goal of these observers is to identify the slip-force curve that corresponds to the current operating condition of the tire and thereby estimate the current limit of the traction force, i.e. the tire-road friction coefficient. A primary disadvantage of the observer based techniques is that they do not work under steady state driving conditions, i.e. when the vehicle speed is constant and the steering wheel angle is close to zero. A minimum acceleration/deceleration or steering of the vehicle is required for tire-road friction coefficient parameter to converge to its correct value. Since the vehicle is not likely to always be accelerating/decelerating or cornering, this means that the friction coefficient cannot be continuously updated. A secondary disadvantage in known observer based techniques is that the slip and force observers are usually based on lateral/longitudinal vehicle models whose predictive outputs mis-predict during extreme combined maneuvers. 
     In contrast to such known observer based techniques, the subject invention system and method presents a tire-vehicle integrated tire-road friction coefficient estimation approach which makes use of sensor information from an intelligent tire and vehicle CAN bus information [as shown in  FIG. 2 ]. The sensor signal  16  from an intelligent tire  12  [ FIG. 1 ] are used to estimate the tire dynamic load (F z )  26  and slip angle  28 . Co-pending U.S. patent application Ser. Nos. 13/609,695 and 61/734,526, respectively incorporated herein, show estimation systems and methods for estimating load and slip angle based on strain sensor detected tire deformation. The vehicle CAN bus information is used to make an estimate of the tire lateral and longitudinal forces (F X , F y ) using a dynamic observer as shown in  FIG. 2 . Thereafter, a sensor fusion approach is used to combine the intelligent tire and vehicle information and make an estimate of the tire-road friction coefficient. The performance of the subject system and method when tested and compared with real experimental data acquired on a test vehicle, demonstrates and verifies the ability of this approach to provide accurate estimation of friction coefficient. 
     Variations in the present invention are possible in light of the description of it provided herein. While certain representative embodiments and details have been shown for the purpose of illustrating the subject invention, it will be apparent to those skilled in this art that various changes and modifications can be made therein without departing from the scope of the subject invention. It is, therefore, to be understood that changes can be made in the particular embodiments described which will be within the full intended scope of the invention as defined by the following appended claims.