The present invention relates generally to a tire monitor for an automotive vehicle and, more specifically, to a system that monitors an abnormal state of a tire of a moving vehicle including but not limited to a significant tire pressure drop, tire imbalance, the presence of a mini tire, severe tire wear and tire tread separation.
Since the tire/road contact patches determine the dynamic behavior of an automobile, tires are an important safety-critical part of an automobile. More specifically, their normality has an impact on the safety, handling and fuel economy of the vehicle, for example:
Among the aforementioned abnormalities of tires, tire pressure drop detection has received attention. Several methods have been set forth to monitor the tire pressure drop of an automotive vehicle without directly using tire pressure sensors. For example, in U.S. Pat. Nos. 4,224,597 and 5,218,862, the ABS wheel speed sensor signals are used to estimate the velocity differences between wheels in order to identify which tire or tires have significant pressure drops. The method described in U.S. Pat. No. 5,604,307 considers preventing a false detection from road condition changes. Another approach using wheel speed sensors estimates the pressure of tires utilizing the relationship between the air pressure and the tire spring constants. The air pressure drop affects the resonance frequencies of tire vibrations. Estimating the tire rotational resonance frequency and the tire rotational spring rate are studied in U.S. Pat. Nos. 5,753,809 and 5,826,207. The success of those two methods depends on the proper road excitations to the rotational mode of the tires, and avoiding data processing during some vehicle operation conditions (for example, in braking and turning).
U.S. Pat. Nos. 4,224,597 and 5,218,862 are valid when the involved vehicles are driven at high speed and at stable driving conditions, i.e., in a straight line without large acceleration, deceleration and braking. Since the driving condition other than the above stable/straight driving condition may generate similar wheel speed differences, differentiating those differences is a challenge. U.S. Pat. Nos. 5,753,809 and 5,826,207 use vibration signals to estimate resonance frequencies, which may not be able to detect any tire pressure drop if the specific vibration mode cannot be excited.
The above-mentioned methods are not able to detect tire pressure drops if the road and the vehicle operating conditions are not favorable enough to excite the involved vibrations. For example, if a tire leaks when driven on a curving road at a high speed, and at the same time the vehicle is braking, the aforementioned algorithms cannot detect the leak until the vehicle reaches the road conditions which allow the system to work.
It would therefore be desirable to provide a system that determines tire pressure drop without a direct pressure sensor and that is capable of being used in a wider variety of conditions and with sufficient accuracy. Because there are sensors other than ABS wheel speed sensors in current vehicles equipped with dynamics control systems, such as yaw stability control, roll stability control, ABS braking and traction control, it is desirable to pursue the potential benefit of using more information than wheel speeds to clearly identify road and driving conditions.
Besides monitoring or detecting the tire pressure drops, it is also desirable to provide a system to detect or monitor other aspects of the tire abnormalities such as, but not limited to, the presence of a mini tire, tire imbalance, tire rolling radius variation due to uneven-distributed vehicle loading, tire wearing, etc. With the addition of sensors in the traditional vehicle dynamics control systems, many difficulties faced by using the traditional approaches to detect those abnormalities can now be overcome. Thus, it is desirable to pursue a system which can achieve the other detections by fully utilizing the information from the extra sensor signals and the calculated vehicle motion state variables.
It is desirable to provide a system which can monitor or detect a variety of tire abnormal states by integrating sensor signals and calculated vehicle motion state variables with various qualitative features of the tire abnormal states.
The present invention provides a device for monitoring the tire abnormal states including, but not limited to tire pressures based on all the available information from a vehicle dynamics control system. More specifically, the present invention may be used to monitor an abnormal state of a tire of a moving vehicle including but not limited to a significant tire pressure drop, tire imbalance, the presence of a mini tire, severe tire wear and tire tread separation. The system may generate digital information for warning and control purposes in an integrated sensing system (ISS) and an integrated actuation system (IAS), which involve using multiple sensor signals and multiple actuators to achieve arbitrated and prioritized control functions related to vehicle dynamics and vehicle active safety. The tire abnormal state monitor sends a warning signal to the display to warn the driver and sends digital flags to the vehicle dynamics control system so that necessary adjustments and modifications may be performed. Systems requiring modification may include but are not limited to antilock braking, yaw stability control, roll stability control, traction control, 4WD control, transmission control and engine control.
In one aspect of the invention, a method of controlling a vehicle includes determining at least one of a tire rolling radius, determining a tire vertical spring rate, determining a tire rotational spring rate, tire imbalance and determining a tire abnormal state in response to the at least one of the tire rolling radius, the tire vertical spring rate, the tire rotational spring rate and tire imbalance. The vehicle is controlled in response to the detected tire abnormal state. Various types of vehicle control may be performed including warning the driver of the abnormality and/or controlling a dynamic control system of the vehicle in response to the detected tire abnormal state.
In a further aspect of the invention, a method of controlling a vehicle includes generating a wheel speed signal, determining at least one of a vehicle longitudinal velocity, a vehicle lateral velocity, and a vehicle vertical velocity, determining at least one of a yaw signal, a roll signal, and a pitch signal. A tire abnormal state is determined in response to the wheel speed, the at least one of the vehicle longitudinal velocity, the lateral vehicle velocity, the vehicle vertical velocity, the at least one of the yaw signal, the roll signal, and the pitch signal. The vehicle is controlled in response to the tire abnormal state.
One advantage of such a system is that it may be used to detect the tire pressure drops regardless of the vehicle operation condition (accelerating, decelerating and braking) and the road condition (straight, curving, rough, smooth, banked or graded). The other advantage of such a system is that it may be used to trigger control adjustment in vehicle stability control systems so as to achieve better control performance.
Another advantage of the system is that the system detects specific tire abnormal states including but not limited to mini tires, tire imbalance, tire variation due to uneven-distributed vehicle loading, tire wear, etc., by checking the quantitative features of several independently calculated tire parameters in an integrated sense. In this way, the multiple causes of the same symptom could be isolated. For example, a tire rolling radius reduction might be any of tire pressure drops, mini tire with normal tire pressure, large vehicle loading with normal tire pressure, and/or large vehicle loading with low tire pressure.
Hence, checking tire rolling radius may not identify which causes the reduction of tire rolling radius. In the integrated approach of the present application, several separately calculated tire parameters may be checked such that the specific abnormality can be identified.
In the following figures, the same reference numerals will be used to identify the same components. The present invention may be used in conjunction with a dynamic control system such as a rollover control system for a vehicle. However, the system may be used as a driver warning device. The present invention will be discussed below in terms of preferred embodiments relating to an automotive vehicle moving in a three-dimensional road terrain. Also, the system may be used with a four-wheel drive or all-wheel drive vehicle. Such a vehicle is generally referred to as a four driven wheel vehicle since each of the wheels is capable of generating longitudinal forces derived from the powertrain.
Referring to
As mentioned above, the system may also be used with driver warning systems including active/semi-active suspension systems; active anti-roll bars, airbags or other safety devices deployed or activated upon sensing predetermined dynamic conditions of the vehicle.
The sensing system 16 is coupled to a control system 18. The sensing system 16 may comprise many different sensors including the sensor set typically found in a roll stability control or a rollover control system (including lateral accelerometer, yaw rate sensor, steering angle sensor and wheel speed sensor which are equipped for a traditional yaw stability control system) together with a roll rate sensor and a longitudinal accelerometer. The various sensors will be further described below. The sensors may also be used by the control system in various determinations such as to determine a lifting event, determine a height and position of a mass, a relative attitude, etc. The wheel speed sensors 20 are mounted at each corner of the vehicle and generate signals corresponding to the rotational speed of each wheel. Sensors 28, 32, 33, 34, 36 and 37 of sensing system 16 may be mounted directly on the center of gravity of the vehicle body, along the directions x,y and z shown in
The angular rate sensors and the accelerometers may be mounted on the vehicle car body along the body frame directions b1,b2 and b3 which are the x-y-z axes of the sprung mass of the vehicle.
The longitudinal acceleration sensor 36 is mounted on the car body located at the center of gravity, with its sensing direction along b1-axis, whose output is denoted as ax. The lateral acceleration sensor 32 is mounted on the car body located at the center of gravity, with its sensing direction along b2-axis, whose output is denoted as ay.
The other frame used in the following discussion includes the road frame, as depicted in
In the following discussion, the Euler angles of the body frame b1b2b3 with respect to the road frame or moving road frame (mrf) r1r2r3 are denoted as θxbr and θybr, which are also called the relative Euler angles (i.e., relative roll and relative pitch angles, respectively).
Referring now to
Controller 26 may include a signal multiplexer 50 that is used to receive the signals from the sensors 28-42. The signal multiplexer 50 provides the signals to sensor signal compensation 52 and a relative attitude determination 54, and to a roll stability control (RSC) feedback control command 56. The relative attitude determination 54 may also be coupled to the RSC feedback command 56. The RSC feedback command 56 may include a torque controller 57. The relative attitude determination may determine roll and pitch angles described in the vehicle roll angle calculator described in U.S. Provisional Applications 60/400,376 and 60/400,172, and in U.S. patent application Ser. No. 10/459,697, the disclosures of which are incorporated herein by reference.
In the preferred embodiment, the sensors are located at the center of gravity of the vehicle. Those skilled in the art will recognize that the sensor may also be located off the center of gravity and translated equivalently thereto.
Lateral acceleration, roll orientation and speed may be obtained using a global positioning system (GPS). Based upon inputs from the sensors, controller 26 may control a safety device 44. Depending on the desired sensitivity of the system-and various other factors, not all the sensors. 28-42 may be used in a commercial embodiment. Safety device 44 may control an airbag 45 or a steering actuator 46A-46 at one or more of the wheels 12a, 12b, 13a, 13b of the vehicle. Also, other vehicle components such as a suspension control 48 may be used to adjust the suspension to prevent rollover.
The controller 26 may also be coupled to a warning device 70. The warning device 70 may be audible, visual, or a combination. The warning device 70 provides an indication of a tire abnormal state to the driver. The tire abnormal state will be described below.
Roll angular rate sensor 34 and pitch rate sensor 37 may sense the roll condition or lifting of the vehicle based on sensing the height of one or more points on the vehicle relative to the road surface. Sensors that may be used to achieve this include but are not limited to a radar-based proximity sensor, a laser-based proximity sensor and a sonar-based proximity sensor. The roll rate sensor 34 may also use a combination of sensors such as proximity sensors to make a roll rate determination.
Roll rate sensor 34 and pitch rate sensor 37 may also sense the roll condition or lifting based on sensing the linear or rotational relative displacement or displacement velocity of one or more of the suspension chassis components. This may be in addition to or in combination with suspension position sensor 42. The position sensor 42, roll rate sensor 34 and/or the pitch rate sensor 37 may include a linear height or travel sensor, a rotary height or travel sensor, a wheel speed sensor used to look for a change in velocity, a steering wheel position sensor, a steering wheel velocity sensor and a driver heading command input from an electronic component that may include steer by wire using a hand wheel or joy stick.
The roll condition or lifting may also be sensed by sensing directly or estimating the force or torque associated with the loading condition of one or more suspension or chassis components including a pressure transducer in an act of air suspension, a shock absorber sensor such as a load sensor 40, a strain gauge, the steering system absolute or relative motor load, the steering system pressure of the hydraulic lines, a tire laterally force sensor or sensors, a longitudinal tire force sensor, a vertical tire force sensor or a tire sidewall torsion sensor. The yaw rate sensor 28, the roll rate sensor 34, the lateral acceleration sensor 32, and the longitudinal acceleration sensor 36 may be used together to determine that the wheel has lifted. Such sensors may be used to determine wheel lift or estimate normal loading associated with wheel lift.
The roll condition of the vehicle may also be established by one or more of the following translational or rotational positions, velocities or accelerations of the vehicle including a roll gyro, the roll rate sensor 34, the yaw rate sensor 28, the lateral acceleration sensor 32, the vertical acceleration sensor 33, a vehicle longitudinal acceleration sensor 36, lateral or vertical speed sensor including a wheel-based speed sensor 20, a radar-based speed sensor, a sonar-based speed sensor, a laser-based speed sensor or an optical-based speed sensor.
Safety device 44 may control the position of the front right wheel actuator 46A, the front left wheel actuator 46B, the rear left wheel actuator 46C, and the right rear wheel actuator 46D. Although as described above, two or more of the actuators may be simultaneously controlled. For example, in a rack-and-pinion system, the two wheels coupled thereto are simultaneously controlled. Based on the inputs from sensors 28 through 42, controller 26 determines a roll condition and/or wheel lift and controls the steering position and/or braking of the wheels.
Safety device 44 may be coupled to a brake controller 60. Brake controller 60 controls the amount of brake torque at a front right brake 62a, front left brake 62b, rear left brake 62c and a rear right brake 62d. Other safety systems such as an antilock brake system 64, a yaw stability control system 66 and a traction control system 68 may also benefit from the knowledge of the roll gradient, roll rate parameter, roll acceleration coefficient, additional mass and position of the mass. This information may impact the control strategy such as an amount of braking may be modified.
Speed sensor 20 may be one of a variety of speed sensors known to those skilled in the art. For example, a suitable speed sensor may include a sensor at every wheel that is averaged by controller 26. The controller 26 may translate the wheel speeds into the speed of the vehicle. Yaw rate, steering angle, wheel speed and possibly a slip angle estimate at each wheel may be translated back to the speed of the vehicle at the center of gravity. Various other algorithms are known to those skilled in the art. Speed may also be obtained from a transmission sensor. For example, if speed is determined while speeding up or braking around a corner, the lowest or highest wheel speed may not be used because of its error. Also, a transmission sensor may be used to determine vehicle speed.
Load sensor 40 may be a load cell coupled to one or more suspension components. By measuring the stress, strain or weight on the load sensor a shifting of the load can be determined.
The roll condition of a vehicle can be characterized by the relative roll angle between the vehicle body and the wheel axle and the wheel departure angle (between the wheel axle and the average road surface). Both the relative roll angle and the wheel departure angle may be calculated in relative roll angle estimation module by using the roll rate and lateral acceleration sensor signals. If both the relative roll angle and the wheel departure angles are large enough, the vehicle may be in either single wheel lifting or double wheel lifting. On the other hand, if the magnitude of both angles is small enough, the wheels are likely all grounded. In case that both of them are not small and the double wheel lifting condition is detected or determined, the sum of those two angles will be used by the feedback control module to compute the desired actuation command for achieving rollover control performance.
The roll condition of a vehicle can be characterized by rolling radius-based wheel departure roll angle, which captures the angle between the wheel axle and the average road surface through the dynamic rolling radii of the left and right wheels when both of the wheels are grounded. Since the computation of the rolling radius is related to the wheel speed and the linear velocity of the wheel, such rolling-radius based wheel departure angle will assume abnormal values when there are large wheel slips. This happens when a wheel is lifted and there is torque applied to the wheel. Therefore, if this rolling radius-based wheel departure angle is increasing rapidly, the vehicle might have lifted wheels. Small magnitude of this angle indicates the wheels are all grounded.
The roll condition of the vehicle can be seen indirectly from the wheel longitudinal slip. If during a normal braking or driving torque the wheels at one side of the vehicle experience increased magnitude of slip, then the wheels of that side are losing longitudinal road torque. This implies that the wheels are either driven on a low mu surface or lifted up. The low mu surface condition and wheel-lifted-up condition can be further differentiated based on the chassis roll angle computation, i.e., in low mu surface, the chassis roll angle is usually very small. Hence, an accurate determination of chassis roll is desired.
The roll condition of the vehicle can be characterized by the normal loading sustained at each wheel. Theoretically, when a normal loading at a wheel decreases to zero, the wheel is no longer contacting the road surface. In this case a potential rollover is underway. Large magnitude of this loading indicates that the wheel is grounded. Normal loading is a function of the calculated chassis roll and pitch angles. Hence, an accurate determination of chassis roll and pitch angles is desired.
The roll condition can be identified by checking the actual road torques applied to the wheels and the road torques, which are needed to sustain the wheels when they are grounded. The actual road torques can be obtained through torque balancing for each wheel using wheel acceleration, driving torque and braking torque. If the wheel is contacting the road surface, the calculated actual road torques must match or be larger than the torques determined from the nonlinear torques calculated from the normal loading and the longitudinal slip at each wheel.
The roll condition of a vehicle can be characterized by the chassis roll angle itself, i.e., the relative roll angle θxr between the vehicle body and the wheel axle. If this chassis roll angle is increasing rapidly, the vehicle might be on the edge of wheel lifting or rollover. Small magnitude of this angle indicates the wheels are not lifted or are all grounded. Hence, an accurate determination of the chassis roll angle is beneficial for determining if the vehicle is in non-rollover events.
The roll condition of a vehicle can also be characterized by the roll angle between the wheel axle and the average road surface, this is called wheel departure angle. If the roll angle is increasing rapidly, the vehicle has lifted wheel or wheels and aggressive control action needs to be taken in order to prevent the vehicle from rolling over. Small magnitude of this angle indicates the wheels are not lifted.
The center of gravity C is also illustrated with nominal mass M. A roll axis is also illustrated at a distance D from the center of gravity. The variable ay is the lateral acceleration.
Referring now to
Another angle of importance is the linear bank angle. The linear bank angle is a bank angle that is calculated more frequently (perhaps in every loop) by subtracting the relative roll angle generated from a linear roll dynamics of a vehicle (see U.S. Pat. No. 6,556,908 which is incorporated by reference herein), from the calculated global roll angle (as the one in U.S. Pat. No. 6,799,092, which is incorporated by reference herein). If all things were slowly changing without drifts, errors or the like, the linear bank angle and reference road bank angle terms would be equivalent.
Referring now to
Referring now to
It is a well known that the tire spring rates are related to the tire air pressures. Low tire pressure may cause changes in the tire rotational and vertical spring rates.
Referring now to
Referring now to
The tire parameters determined in tire parameter determination 78 that may be used in the tire abnormal determination 80 include but are not limited to steady-state rolling radius of the tire, rotational spring rate of the tire, vertical spring rate of the tire, and imbalance strength of the tire.
Not all of the tire parameters are required for each of the abnormal determinations. Specific examples are set forth below.
Referring now to
Referring now to
Referring now to
The variable wsi is the ith wheel speed sensor output for i=0,1,2,3 (corresponding to front left, front right, rear left and rear right wheel respectively). Notice that ws0, ws1, ws2 and ws3 are related to the rotational speeds of wheels through the gains which reflect the static rolling radii of the wheels. The rotation speeds are defined along the longitudinal directions of the wheels.
Using the calculated vehicle longitudinal and lateral velocities from ISS 76, and the kinematical relationships of the calculated signals and the measured signals, the longitudinal and lateral velocities at the spindles of the wheels but along the sensor frame's x, y and z axes can be expressed as in the following:
vx0SF=vxISS−ωhd zstf, vy0SF=vyISS+ωzsbf, vz0SF=vzISS+ωxstf−ωysbf,
vx1SF=vxISS=ωzstf, vy1SF=vyISS+ωzsbf, vz1SF=vzISS−ωxstf−ωysbf,
vx2SF=vxISS−ωzstr, vy2SF=vyISS+ωzsbr, vz2SF=vzISS+ωxstr+ωysbr,
vx3SF=vxISS+ωzstr, vy3SF=vyISS+ωzsbr, vz3SF=vzISS−ωxstr+ωysbr, (1)
where tf and tr are the half tracks at the front and rear axle respectively, bf and br are the distances from the sensor location to the front and rear axle respectively.
When the vehicle is turning or braking, the vehicle body has a slight tilt with respect to the road. Hence, the wheel speed sensor signals are usually different from the calculated variables in Equation (1). These differences can be eliminated by using the relative attitudes calculated in the RAD unit and the sensor misalignments calculated in the SSC unit. The relative roll and pitch angles as θxr,θyr and the sensor misalignment from the sensor frame to the vehicle body frame are Δθxsb,Δθysb,Δθzsb, respectively, then through Euler transformation, the velocities at the spindles along the moving road-frame (MRF) can be determined as in the following:
vxiMRF=Eulertfx(vxiSF, vyiSF, vziSF,θxr+Δθxsb,θyr+Δθysb,Δθzsb)
vyiMRF=Eulertfy(vxiSF, vyiSF, vziSF,θxr+Δθxsb,θyr+Δθysb,Δθzsb)
vziMRF=Eulertfz(vxiSF, vyiSF, vziSF,θxr+Δθxsb,θyr+Δθysb,Δθzsb) (2)
for i=0,1,2,3 (corresponding to front left, front right, rear left and rear right wheel, respectively). Later the integration of moving road references may be referred to as Zb, which is the vertical displacement of the point on the vehicle body where the suspension is, connected thereto. Then, the following wheel longitudinal velocities for a front steering vehicle are:
v0MRF=vx0MRF cos δf+vy0MRF sin δf
v1MRF=vx1MRF cos δf+vy1MRF sin δf
v2MRF=vx2MRF
v3MRF=vx3MRF (3)
or the following for a rear steering vehicle
v0MRF=vx0MRF
v1MRF=vx1MRF
v2MRF=vx2MRF cos δr+vy2MRF sin δr
v3MRF=vx3MRF cos δr+vy3MRF sin δr (4)
or the following for a four wheel steering vehicle
v0MRF=vx0MRF cos δf+vy0MRF sin δf
v1MRF=vx1MRF cos δf+vy1MRF sin δf
v2MRF=vx2MRF cos δr+vy2MRF sin δr
v3MRF=vx3MRF cos δr+vy3MRF sin δr (5)
From the above variables, the tire rolling radius may be determined in step 124. The computation of Equation (5) may also be expressed as the following for the ith wheel
where vcpi is the sliding velocity of the contact patch between the ith wheel and the road, wsi is the wheel speed sensor signal, and r0i is the nominal rolling radius of the ith wheel, and ri is the steady state rolling radius of the ith wheel.
If the wheels are all rolling without slipping, based on Equations (5) and (6), the steady state rolling radius ri of the ith wheel can be calculated as:
For robust implementation, the steady state rolling radius is calculated by averaging the ri value over a long period of time when the driving conditions permit the determination. Such driving conditions are called the screening conditions. If the number of samples in the averaging process is N, then the following algorithm is performed:
where the subscript k indicates the current time instant of the regular samples, the subscript n indicates the current time instant when the screening condition is satisfied, the subscript n−1 indicates the past time instant when the screening condition is satisfied, R and {overscore (R)} are the lower and upper bounds of the rolling radius. When the averaging achieves N, the final steady state rolling radius of the ith wheel can be further obtained as in the following:
With the above calculated rolling radius, the compensated wheel speed sensor signals can be expressed as:
The screening conditions used in the above computations might include multiple conditions. For example, one screening condition for activating the computation of the steady state rolling radius may be that the ith wheel does not experience vertical oscillation, i.e., the ith wheel taking-off angle
is very small, or the wheel is well contacted with the road surface, or the wheel is not driven on a rough road, gravel road or off-road.
Another screening condition for activating the computation of the steady state rolling radius might be that the wheel is not slipping in longitudinal direction, which can be determined by comparing the following longitudinal slip ratio with a threshold:
Yet another screening condition for activating the computation of the steady state rolling radius might be that the tire is not being applied to large driving/braking torques, which can be calculated based on the braking pressure and the driving torque from the powertrain.
In step 126 the tire rotational spring rate may be determined. The tire and wheel assembly shown in
The variables Io and Ii are the rolling momentum inertias of the inner and outer masses. The air in the tire generates elasticity effects in between the inner and outer masses along the rotational, vertical and lateral directions. Such elasticity effects are modeled with a rotational spring with spring rate Kr and a vertical spring with spring rate Kv. There is a torque τroad applied to the outer piece from the road and a driving torque τdrive applied to the inner piece from the power. The wheel speed sensor measures the rotation speed between the inner and the out masses.
If the rotational damping between the inner and the outer mass is Dr, by using Newton's law, the rotational acceleration of the outer mass may be calculated as:
and the rotational acceleration of the inner mass may be calculated as
where ws is the wheel speed sensor output and r0 is the nominal rolling radius of the tire.
Since the difference between the rotational accelerations of the inner mass and the outer mass is the same as the derivative of the wheel speed sensor signals, the following dynamic relationship may be developed:
Consider a band-pass filter B with its center frequency around 40 Hz. For example, one of such filter of the fourth order can be described as the following in z-transform:
and consider another washout integration filter T. For example, one of such filter of the first order can be described as the following in z-transform
with properly chosen filter coefficients ni and di for i=1,2, . . . , 5. T(z)=1 may be set so that there is no integration in the wheel speed signals and the computation will still be valid since when differentiating Equation (14), a similar equation is true except that
in Equation (14) will be replaced by
The signal generated by passing the wheel speed sensor signal ws through these two filters in Equations (14) and (15) sequentially is a signal which is the integral of the wheel speed sensor signal but with frequency contents limited to the frequency interval defined by the band-pass filter B. That signal is wsf, i.e., in z-domain:
wsf=B(z)T(z)ws (18)
Such a signal wsf in Equation (18) is the signal with frequency contents limited within the frequency interval filter defined by the band-pass filter.
The variables needed to conduct tire rotational spring rate determination are determined. The specific method of interest is the two parameter conditional least square (CLS) method.
Let N be the total number of samples in the least square method. The following cumulative sums are determined when the screening condition for determining tire rotational spring rate is satisfied and the number of the samples used is less than the total number N of the samples
where the subscript k,k−1 and k−2 indicate the current, the first past and the second past time instant, or the timing kΔT, (k−1)ΔT and (k−2)ΔT with ΔT being the sampling time.
As the cumulative sums collect N samples, the following computation generates two intermediate parameters θ1 and θ2. In the algorithm amin is used to bound other intermediate variables such as Dθand a22
After θ1 and θ2 are calculated, the tire rotational spring rate Kr is ready to be determined through the following algorithm:
where ΔT is the sampling time used, for example, ΔT=2 ms.
In step 128 the tire vertical spring rate is determined in step 128. A vertical dynamics of the tire/wheel assembly can be similarly modeled as the rotational dynamics were performed above in step 126. The inner piece has a mass Mi and the outer piece has a mass Mo. The variable zsh is the suspension height, which is measured by a suspension height sensor, and ztd being the tire vertical deflection due to air compression (the vertical stiffness Kv). The vertical acceleration of the inner mass can be computed by balancing the vertical forces applied to the tire, namely, the suspension force and the tire normal force, as in the following:
The variable zb is the vertical displacement of the point on the vehicle body where the suspension is connected. The vehicle state variables may be calculated in the ISS system. If the wheel of interest is the ith wheel, then zbi can be obtained by integrating the vertical velocity vziSF as calculated in Equation (1).
The vertical acceleration of the inner mass may be. alternatively described using zb and the suspension height zsh as:
Av-inner={umlaut over (z)}b−{umlaut over (z)}sh (23)
and the tire deflection ztd can be determined as
ztd=zb−zsh−v (24)
Therefore:
where v is the vertical road profile.
Since Equation (25) is true for specific frequency range, hence it is true for some band-pass filtered signals. Let B′ be a band-pass filter and denote the signal generated by passing the suspension height through this filter as zshf, i.e., in z-domain:
zshf=B′(z)zsh (26)
then such a filtered signals must satisfy the following equation:
The vertical road profile v is a random variable, whose averaging effect can be thought around zero, hence from a long term point of view, it may be assumed that:
That is, the following is true for the long term:
Consider in each time instant k, the above equation might be expressed as:
(zshf)k+φ1(zshf)k-1+φ2(zshf)k-2=fk-1({umlaut over (z)}b,{dot over (z)}b,zb) (30)
and the two unknown parameters may be determined through the following two parameter conditional least square method. The variable N is the total number of samples in the least square method. First, the following cumulative sum is determined when the screening condition for determining tire vertical spring rate is satisfied and the number of the samples used is less than the total number N of the samples:
As the cumulative sums collect N samples, the following computation generates two intermediate parameters φ1 and φ2. In the algorithm cmin used to bound some other intermediate variables such as Dφand c22
After φ1 and φ2 are calculated, the tire rotational spring rate Kv is ready to be determined through the following algorithm:
where Kv and {overscore (K)}v are the lower and upper bounds of the vertical spring rate of a tire, respectively.
The screening conditions to activate the computation of the vertical tire spring rate include that the tire is not heavily braked, the wheel taking-off angle as in Equation (11) is small, the wheel longitudinal slip ratio as in Equation (12) is small, the suspension height is not constant, etc.
In step 130 the imbalance strength S may be determined in step 130. The case where there is an imbalanced mass in the wheel/tire assembly is shown in
With increase of the tire rotational speed, the force applied to the inner piece in the vertical direction may be calculated as:
where θ0 is the initial position angle of the imbalanced mass in the tire outer piece with respect to the horizontal plane, ws is the wheel speed sensor output and r0 is the nominal rolling radius used to convert the wheel speed sensor output into an angular velocity of the tire.
Then the following variable χ is computed:
then based on the vertical dynamics of the tire/wheel inner piece, during the rotation of the imbalanced mass,
By differentiating Equation (37),
then the imbalance strength can be calculated as:
An implemented algorithm reflecting the formula in Equation (39) may be expressed in the following through an averaging process:
When the averaging process achieves the predefined number N of the sample points, the imbalance strength can be obtained
If the tire derivative of the wheel speed sensor signal during certain conditions is almost zero, then Equation (39) can be further simplified as:
The screening conditions for activating the computation of the imbalance strength may include that the vehicle speed is greater than a threshold, the lift angle of the wheel is small (guarantee that the tire contacts with the road), the wheel is not applied to large driving or braking torques, the vehicle is in steady state driving (no aggressive accelerations in both longitudinal and lateral directions).
In step 132, the tire abnormal state detection utilizes the variables already calculated to decide whether the tires have an abnormality. There are two sets of tire abnormal states. One is inherent to the tire which are directly related to the structure of the tire, which may be referred to as the inherent abnormal states. The other is due to the operation condition changes in the other parts of the vehicle, which may be called parasite abnormal states.
The inherent abnormal states might include, but are not limited to tire pressure drop, tire imbalance, tire wear, and tire tread separation.
The parasitic abnormal states might include, but are not limited to tire rolling radius variation due to vehicle loading variation, tire rolling radius variation due to vehicle loading distribution variation, tire rolling radius variation due to the installation of mini tire or other off-spec tires, and high tire temperature during brake due to a sticking brake pad or other non-rubber related problems.
Therefore, it is desirable to separate the inherent tire abnormal states and the parasite tire abnormal states.
In
Referring to
Referring now to
Referring now to
Referring back to step 182, if the tire rotational spring rate reduces to below a lower bound and the rolling radius and the vertical spring rate are about-normal in step 186, tire tread separation may be detected in step 188.
Referring back to step 184, if tread wear is found and a vehicle is detected to have wear in rear axle or tread separation in rear axle in step 190, the vehicle over-steer characteristics will be re-registered in the vehicle stability control system and certain over-steer control thresholds will be adjusted so that the over-steer control is more sensitive in step 192. That is, earlier activations are possible to reduce potential chance for the vehicle to spin out.
Referring now to
In step 204, if the two rear tires (rear axle) both have significant reduction in rolling radius in step 206, but the rotational and vertical spring rates are normal, then most likely there is a significant trunk loading in the vehicle as indicated in step 210.
If a vehicle is detected to have heavy loading in the rear axle, the vehicle over-steer characteristics will be re-registered in the vehicle stability control system and certain over-steer control threshold will be adjusted in step 212.
If all four tires have significant reduction in rolling radius, but the rotational and vertical spring rates are all normal, then there is likely a significant but balanced loading in the vehicle in step 216.
Referring back to
Thus as can be seen, specific tire abnormal states such as but not limited to mini-spare detection, tire imbalance, and tire variation due to uneven vehicle loading may be determined using the tire parameters. Thus, multiple causes of a symptom may be isolated to one cause.
While particular embodiments of the invention have been shown and described, numerous variations and alternate embodiments will occur to those skilled in the art. Accordingly, it is intended that the invention be limited only in terms of the appended claims.