Dynamic-based method of estimating the absolute roll angle of a vehicle body

Abstract

The absolute roll angle of a vehicle body is estimated by blending two preliminary roll angle estimates based on their frequency so that the blended estimate continuously favors the more accurate of the preliminary roll angle estimates. A first preliminary roll angle estimate based on the measured roll rate is improved by initially compensating the measured roll rate for bias error using roll rate estimates inferred from other measured parameters. And a second preliminary roll angle estimate is determined according to the sum of the road bank angle and the relative roll angle. The blended estimate is used to estimate the actual lateral acceleration, the lateral velocity and side-slip angle of the vehicle, which are used in rollover detection and other various other control applications.

Description

TECHNICAL FIELD

The present invention relates to estimation of the absolute roll angle of a vehicle body for side airbag deployment and/or brake control, and more particularly to an improved dynamic-based estimation method.

BACKGROUND OF THE INVENTION

A number of vehicular control systems including vehicle stability control (VSC) systems and rollover detection/prevention systems utilize various sensed parameters to estimate the absolute roll angle of the vehicle body—that is, the angle of rotation of the vehicle body about its longitudinal axis relative to the level ground plane. In addition, knowledge of absolute roll angle is required to fully compensate measured lateral accelerometer for the effects of gravity when the vehicle body is inclined relative to the level ground plane.

In general, the absolute roll angle of a vehicle must be estimated or inferred because it cannot be measured directly in a cost effective manner. Ideally, it would be possible to determine the absolute roll angle by simply integrating the output of a roll rate sensor, and in fact most vehicles equipped with VSC and/or rollover detection/prevention systems have at least one roll rate sensor. However, the output of a typical roll rate sensor includes some DC bias or offset that would be integrated along with the portion of the output actually due to roll rate. For this reason, many systems attempt to remove the sensor bias prior to integration. As disclosed in the U.S. Pat. No. 6,542,792 to Schubert et al., for example, the roll rate sensor output can be dead-banded and high-pass filtered prior to integration. While these techniques can be useful under highly transient conditions where the actual roll rate signal is relatively high, they can result in severe under-estimation of roll angle in slow or nearly steady-state maneuvers where it is not possible to separate the bias from the portion of the sensor output actually due to roll rate.

A more effective approach, disclosed in the U.S. Pat. Nos. 6,292,759 and 6,678,631 to Schiffmann, is to form an additional estimate of roll angle that is particularly reliable in slow or nearly steady-state maneuvers, and blend the two roll angle estimates based on specified operating conditions of the vehicle to form the roll angle estimate that is supplied to the VSC and/or rollover detectior/prevention systems. In the Shiffmann patents, the additional estimate of roll angle is based on vehicle acceleration measurements, and a coefficient used to blend the two roll angle estimates has a nominal value except under rough-road or airborne driving conditions during which the coefficient is changed to take into account only the estimate based on the measured roll rate.

Of course, any of the above-mentioned approaches are only as good as the individual roll angle estimates. For example, the additional roll angle estimate used in the above-mentioned Schiffmann patents tends to be inaccurate during turning maneuvers. Accordingly, what is needed is a way of forming a more accurate estimate of absolute roll angle.

SUMMARY OF THE INVENTION

The present invention is directed to an improved method of estimating the absolute roll angle of a vehicle body under any operating condition, including normal driving, emergency maneuvers, driving on banked roads and near rollover situations. The roll angle estimate is based on typically sensed parameters, including roll rate, lateral acceleration, yaw rate, vehicle speed, and optionally, steering angle and longitudinal acceleration. Roll rate sensor bias is identified by comparing the sensed roll rate with roll rate estimates inferred from other measured parameters for fast and accurate removal of the bias. A first preliminary estimate of roll angle is determined according to the sum of the road bank angle and the body roll angle relative to the road. The road bank angle is estimated based on a kinematic relationship involving lateral acceleration, yaw rate, vehicle speed, and steering wheel angle, and the roll angle relative to the road is estimated based on lateral acceleration and the vehicle roll gain. The final or blended estimate of roll angle is then determined by blending the first preliminary estimate with a second preliminary estimate based on the bias-corrected measure of roll rate. In the blending process, the relative weighting between two preliminary roll angle estimates depends on their frequency so that the final estimate continuously favors the more accurate of the preliminary estimates. The blended estimate is used for several purposes, including estimating the lateral velocity and side-slip angle of the vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagram of a vehicle during a cornering maneuver on a banked road;

FIG. 2 is a diagram of a system for the vehicle of FIG. 1, including a microprocessor-based controller for carrying out the method of this invention; and

FIG. 3 is a flow diagram representative of a software routine periodically executed by the microprocessor-based controller of FIG. 2 for carrying out the method of this invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT

Referring to FIG. 1, the reference numeral 10 generally designates a vehicle being operated on a road surface 12. In the illustration, the road surface 12 is laterally inclined (i.e., banked) relative to the level ground plane 14 by an angle φ_bank. Additionally, the body 16 of vehicle 10 has a roll angle φ_rel relative to the road surface 12 due to suspension and tire compliance. The total or absolute roll angle of vehicle body 16, denoted herein as φ_tot, can therefore be expressed as:

φ_tot=φ_bank+φ_ret  (1)

If the roll rate of vehicle 10 about its longitudinal axis is measured, an estimate φ_eω the total roll angle φ_tot can be determined in principle by integrating the measured roll rate, as follows:

$\begin{array}{cc}{\phi }_{e\omega }\left(t\right)={\int }_0^t{\omega }_m\left(\tau \right)\tau & \left(2\right)\end{array}$

where t denotes time and ω_m is the measured roll rate. Unfortunately, the output of a typical roll rate sensor includes some bias error that would be integrated along with the portion of the output actually due to roll rate. Thus, pure integration of the measured roll rate has infinite sensitivity to the bias error because the error is integrated over time. When dead-banding and high-pass (i.e., wash-out) filtering are used to compensate for the bias error, there is still a conflict between the immunity to bias and the ability to track slowly-varying (or constant) roll angles because the bias compensation also reduces the portion of the signal actually due to roll rate. As a result, a roll angle estimate based on roll rate integration is reasonably good during quick transient maneuvers, but less accurate during slow maneuvers or in nearly steady-state conditions when the roll angle changes slowly. As explained below, one aspect of the present invention is directed to an improved method of compensating for the bias error in a measured roll rate signal without substantially diminishing the portion of the signal actually due to roll rate.

An alternative way of determining the total roll angle φ_tot is to sum individual estimates of bank angle bank and relative roll angle φ_rel in accordance with equation (1).

The relative roll angle φ_rel can be estimated as:

φ_rel=−R_gaina_ym  (3)

where a_ym is the lateral acceleration measured at the vehicle's center-of-gravity, and R_gain is the roll gain of vehicle 10. The roll gain R_gain can be estimated for a given vehicle as a function of the total roll stiffness of the suspension and tires, the vehicle mass, and distance from the road surface 12 to the vehicle's center-of-gravity.

The bank angle φ_bank can be estimated based on the kinematic relationship between lateral acceleration a_ym and other measured parameters. Specifically, the lateral acceleration a_ym can be expressed in terms of the total roll angle φ_tot as follows:

a _ym ={dot over (v)} _y +v _x Ω−g sin φ_tot  (4)

where v_y is the lateral velocity of vehicle center-of-gravity, v_x is the vehicle longitudinal velocity, Ω is vehicle yaw rate, and g is the acceleration of gravity (9.806 m/s²). The sign convention used in equation (4) assumes that lateral acceleration a_ym and yaw rate Ω are positive in a right turn, but the roll angle φ_tot due to the turning maneuver is negative. The same sign convention is used in equation (3).

In most instances, sin φ_tot can be closely approximated by the sum (φ_rel+sin φ_bank) because φ_rel will be small (say, less than 7 degrees) and bank will not exceed 15 degrees. Hence, equation (4) can be reformulated as:

a _ym +gφ _rel ={dot over (v)} _y +v _x Ω−g sin φ_bank  (5)

In equation (5), the term ({dot over (v)}_y+v_xΩ) is the cornering component of the measured lateral acceleration a_ym, and the term (−g sin φ_bank) is the bank angle component of a_ym, also referred to herein as bank acceleration a_ybank. Therefore, the term on the left side of the equation—that is, (a_ym+gφ_rel)—is the measured lateral acceleration compensated for the effect of relative roll angle φ_rel, also referred to herein as a_ycomp.

If the derivative of lateral velocity (i.e., {dot over (v)}_y) is relatively small, the bank acceleration a_ybank (that is, −g sin φ_bank) can be estimated by low-pass filtering the expression:

a_ym+gφ_rel−v_xΩ or a_ycomp−v_xΩ  (6)

Thus, bank angle φ_bank can be estimated using equation (6) in a system where v_x and Q are measured in addition to a_ym.

An advantage of estimating the total roll angle BOW as the sum of φ_bank and φ_rel per equation (1) is that φ_rel tends to be substantially larger than φ_bank in most driving conditions. This is significant because φ_rel is reasonably accurate in both steady-state and transient driving conditions, and this accuracy is reflected for the most part in the sum (φ_bank+φ_rel). Of course, in transient conditions on a significantly banked road, the estimation inaccuracy of φ_bank (due to the assumption that the derivative of lateral velocity is negligible) will also be reflected in the sum (φ_bank+φ_rel). Thus, the estimation of φ_tot based on equation (1) tends to be reasonably accurate except under transient conditions on a significantly banked road.

In summary, the foregoing methods of estimating absolute roll angle each have significant limitations that limit their usefulness. As explained above, a roll angle estimate based on roll rate integration is reasonably good during quick transient maneuvers, but less accurate during slow maneuvers or in nearly steady-state conditions when the roll angle changes slowly due to inability to separate the bias error from the portion of the signal actually due to roll rate. On the other hand, the roll angle estimate based on the sum of φ_bank and φ_rel according to equation (1) is reasonably good during nearly steady-state or low frequency maneuvers, and even during quick maneuvers performed on level roads, but unreliable during quick transient maneuvers performed on banked roads or when roll angle is induced by road bumps, which usually elicit fairly quick transient responses.

It can be seen from the above that the two roll angle estimation methods are complementary in that conditions that produce an unreliable estimate from one estimation method produce an accurate estimate from the other estimation method, and vice versa. Accordingly, the method of this invention blends both estimates in such a manner that the blended roll angle estimate is always closer to the initial estimate that is more accurate.

FIG. 2 is a diagram of an electronic control system 20 installed in vehicle 10 for enhancing vehicle stability and occupant safety. For example, the system 20 may include a vehicle stability control (VSC) system for dynamically activating the vehicle brakes to enhance stability and reduce the likelihood of rollover, and a supplemental restraint system (SRS) for deploying occupant protection devices such as seat belt pretensioners and side curtain air bags in response to detection of an impending rollover event. System sensors include a roll rate sensor 22 responsive to the time rate of angular roll about the vehicle longitudinal axis, a lateral acceleration sensor 24 responsive to the vehicle acceleration along its lateral axis, a yaw rate sensor 26 responsive to the time rate of yaw motion about the vehicle yaw axis, and at least one wheel speed sensor 28 for estimating the vehicle velocity along its longitudinal axis. Optionally, the system 20 additionally includes a hand-wheel sensor 30 responsive to the vehicle steering angle and a longitudinal acceleration sensor 32 responsive to the vehicle acceleration along its longitudinal axis. In practice, ordinary VSC systems include most if not all of the above sensors. Output signals produced by the sensors 22-32 are supplied to a microprocessor-based controller 34 which samples and processes the measured signals, carries out various control algorithms, and produces outputs 36 for achieving condition-appropriate control responses such as brake activation and deployment of occupant restraints. Of course, the depicted arrangement is only illustrative; for example, the functionality of controller 34 may be performed by two or more individual controllers if desired.

FIG. 3 depicts a flow diagram representative of a software routine periodically executed by the microprocessor-based controller 34 of FIG. 2 for carrying out the method of the present invention. The input signals read at block 40 of the flow diagram include measured uncompensated roll rate φ_m—un, measured lateral acceleration a_ym, yaw rate Ω, vehicle speed v_x, and optionally, hand-wheel (steering) angle HWA and measured longitudinal acceleration a_xm. It is assumed for purposes of the present disclosure that the yaw rate Ω and lateral acceleration a_ym input signals have already been compensated for bias error, as is customarily done in VSC systems. Furthermore, it is assumed that all the input signals have been low-pass filtered to reduce the effect of measurement noise.

Block 42 pertains to systems that include a sensor 32 for measuring longitudinal acceleration a_xm, and functions to compensate the measured roll rate ω_m—un for pitching of vehicle 10 with respect to the horizontal plane 14. Pitching motion affects the roll rate detected by sensor 22 due to cross coupling between the yaw rate and roll rate vectors when the vehicle longitudinal axis is inclined with respect to the horizontal plane 14. This occurs, for example, during driving on a spiral ramp. Under such conditions the vertical yaw rate vector has a component along the longitudinal (i.e. roll) axis, to which sensor 22 responds. This component is not due to change in roll angle and should be rejected before the roll rate signal is further processed. In general, the false component is equal to the product of the yaw rate Ω and the tangent of the pitch angle θ. The absolute pitch angle θ is estimated using the following kinematic relationship:

a _xm ={dot over (v)} _x −v _y Ω+g sin θ  (7)

where a_xm is the measured longitudinal acceleration, {dot over (v)}_x is the time rate of change in longitudinal speed v_x, v_y is the vehicle's side-slip or lateral velocity, Ω is the measured yaw rate, and g is the acceleration of gravity. Equation (7) can be rearranged to solve for pitch angle θ as follows:

$\begin{array}{cc}\theta ={\sin }^{-1}\frac{a_{\mathrm{xm}}-{\stackrel{.}{v}}_x=v_y\Omega }{g}& \left(8\right)\end{array}$

The term {dot over (v)}_x is obtained by differentiating (i.e., high-pass filtering) the estimated vehicle speed v_x. If the lateral velocity v_y is not available, the product (v_y Ω) can be ignored because it tends to be relatively small as a practical matter. However, it is also possible to use a roll angle estimate to estimate the lateral velocity v_y, and to feed that estimate back to the pitch angle calculation, as indicated by the dashed flow line 60. Also, the accuracy of the pitch angle calculation can be improved by magnitude limiting the numerator of the inverse-sine function to a predefined threshold such as 4 m/s². The magnitude-limited numerator is then low-pass filtered with, for example, a second-order filter of the form b_nf²/(s²+2ζb_nf+b_nf²), where b_nf is the undamped natural frequency of the filter and ζ is the damping ratio (example values are b_nf=3 rad/sec and ζ=0.7). Also, modifications in the pitch angle calculation may be made during special conditions such as heavy braking when the vehicle speed estimate v_x may be inaccurate. In any event, the result of the calculation is an estimated pitch angle θ_e, which may be subjected to a narrow dead-zone to effectively ignore small pitch angle estimates. Of course, various other pitch angle estimation enhancements may be used, and additional sensors such as a pitch rate sensor can be used to estimate θ by integration.

Once the pitch angle estimate θ_e is determined, the measured roll rate is corrected by adding the product of the yaw rate Ω and the tangent of the pitch angle θ_e to the measured roll rate Ω_m—^un to form the pitch-compensated roll rate Ω_m as follows:

ω_m=ω_m—un+Ω tan θ_e  (9)

Since in nearly all cases, the pitch angle de is less than 20° or so, equations (8) and (9) can be simplified by assuming that sin θ≅tan θ≅θ. And as mentioned above, the measured roll rate ω_m—un can be used as the pitch-compensated roll rate ω_m if the system 20 does not include the longitudinal acceleration sensor 32.

Block 44 is then executed to convert the roll rate signal ω_m into a bias-compensated roll rate signal ω_m—cor suitable for integrating. In general, this is achieved by comparing ω_m with two or more roll rate estimates obtained from other sensors during nearly steady-state driving to determine the bias, and then gradually removing the determined bias from ω_m.

A first roll rate estimate ω_eay is obtained by using equation (3) to calculate a roll angle φ_eay corresponding to the measured lateral acceleration a_ym, and differentiating the result. However, a_ym is first low-pass filtered to reduce the effect of measurement noise. Preferably, the filter is a second-order filter of the form b_nf²/(s²+2ζb_nf+b_nf²), where b_nf is the un-damped natural frequency of the filter and ζ is the damping ratio (example values are b_nf=20 rad/s and ζ=0.7). And differentiation of the calculated roll angle φ_eay is achieved by passing φ_eay through a first-order high-pass filter of the form b_fs/(s+b_f), where b_f is the filter cut off frequency (an example value is b_f=20 rad/sec). This high-pass filter can be viewed as a combination of a differentiator, s, and a low-pass filter, b/(s+b).

A second roll rate estimate φ_ek is obtained by using the kinematic relationship of equation (4) to calculate a roll angle φ_ek and differentiating the result. The derivative of lateral velocity, {dot over (v)}_y, is neglected since near steady-state driving conditions are assumed. Accordingly, φ_ek is given as:

$\begin{array}{cc}{\phi }_{\mathrm{ek}}={\sin }^{-1}\frac{{\left(v_x\Omega -a_{\mathrm{ym}}\right)}_{\mathrm{filt}}}{g}& \left(10\right)\end{array}$

As indicated in the above equation, the numerator (v_xΩ−a_ym) of the inverse sine function is also low-pass filtered, preferably with the same form of filter used for a_ym in the preceding paragraph. As a practical matter, the inverse sine function can be omitted since the calculation is only performed for small roll angles (less than 3° or so). Differentiation of the calculated roll angle trek to produce a corresponding roll rate ω_ek is achieved in the same way as described for roll angle φ_eay in the preceding paragraph.

Once the roll rate estimates ω_eay and ω_ek have been calculated, a number of tests are performed to determine their stability and reliability. First, the absolute value of each estimate must be below a threshold value for at least a predefined time on the order of 0.3-0.5 sec. Second, the absolute value of their difference (that is, |_eay−ω_ek|) must be below another smaller threshold value for at least a predefined time such as 0.3-0.5 sec. And finally, the absolute value of the difference between the measured lateral acceleration and the product of yaw rate and vehicle speed (that is, |a_ym−v_xΩ|) must be below a threshold value such as 1 m/sec² for at least a predefined time such as 0.3-0.5 sec. Instead requiring the conditions to be met for a predefined time period, it is sufficient to require that the signal magnitudes have a rate of change that is lower than a predefined rate.

When the above conditions are all satisfied, the roll rate estimates φ_eay and ω_ek are deemed to be sufficiently stable and reliable, and sufficiently close to each other, to be used for isolating the roll rate sensor bias error. In such a case, inconsistencies between the estimated roll rates and the measured roll rate are considered to be attributable to roll rate sensor bias error. First, the difference Δω_m—ay between the measured roll rate am and the estimated roll rate ω_eay is computed and limited in magnitude to a predefined value such as 0.14 rad/sec to form a limited difference Δω_m—ay—lim. Then the roll rate sensor bias error ω_bias is calculated (and subsequently updated) using the following low-pass filter function:

ω_bias(t_i+1)=(1−bΔt)ω_bias(t_i)+bΔtΔω_m—ay—lim(t_i)  (11)

where t_i+1 denotes the current value, t_i denotes a previous value, b is the filter cut off frequency (0.3 rad/sec, for example), and Δt is the sampling period. The initial value of ω_bias (that is, ω_bias (t)) is either zero or the value of ω_bias from a previous driving cycle. The roll rate bias error ω_bias is periodically updated so long as the stability and reliability conditions are met, but updating is suspended when one or more of the specified conditions is not satisfied. As a practical matter, updating can be suspended by setting b=0 in equation (11) so that ω_bias(t_i+1)=ω_bias(t_i). Finally, the calculated bias error ω_bias is subtracted from the measured roll rate ω_m, yielding the corrected roll rate ω_m—cor. And if desired, a narrow dead-band may be applied to ω_m—cor to minimize any remaining uncompensated bias.

The blocks 46 and 48 are then executed to estimate bank acceleration a_ybank by calculating a low-pass filtered version of expression (6) similar to the calculation of ω_bias in equation (11). Since expression (6) assumes that the derivative of lateral velocity is negligible, the block 46 first determines a bank filter index bfi that reflects the degree to which this assumption is correct, and the low-pass filter gain b_bf depends on the index bfi. In general, the index bfi has a value of one when vehicle 10 is in nearly steady-state condition in terms of yaw motion, and a value of zero when vehicle 10 is in a transient yaw maneuver. When bfi has a value of one, the filter gain b_bf is relatively high for rapid updating the bank acceleration estimate; but when bfi has a value of zero, the filter gain b_bf is relatively low for slow updating the bank acceleration estimate.

Three conditions are checked to determine whether vehicle 10 is in a nearly steady-state condition in terms of yaw motion. First, magnitude of the rate of change in hand wheel angle (HWA) must be below a threshold value such as 30 deg/sec²≅0.52 rad/sec. As a practical matter, rate of change in HWA can be obtained by passing HWA through a high-pass filter function of the form bs/(s+b) where s is the Laplace operand and b is the filter's cut off frequency. If the input HWA is not available, an alternate condition is that the rate of change of measured lateral acceleration a_ym must be below a threshold such as 5.0 m/sec³. Second, the magnitude of the product of vehicle speed and yaw rate (i.e., |v_xΩ|) must be below a threshold value such as 4 m/sec². And third, the magnitude of the rate of change of the product of vehicle speed and yaw rate (that is, |d(v_xΩ)/dt|) must be below a threshold such as 3 m/sec². Here again, the rate of change of the product v_xΩ can be obtained by passing v_xΩ through a high-pass filter function of the form bs/(s+b) where s is the Laplace operand and b is the filter's cut off frequency. If the three conditions are all satisfied for a specified time period such as 0.5 sec., vehicle 10 is deemed to be in a steady-state condition, and the bank filter index bfi is set to one to establish a relatively high filter gain b_bf such as 1.0 rad/sec. Otherwise, the bank filter index bfi is set to zero to establish a relatively low filter gain b_bf such as 0.25 rad/sec.

As explained above, the bank acceleration a_ybank is the component of the measured lateral acceleration a_ym due to bank angle φ_bank, and is equal to −g sin φ_bank. Also, a_ycomp is the measured lateral acceleration, compensated for the effect of relative roll angle φ_rel, and is equal to (a_ym+gφ_rel) In general, the bank acceleration a_ybank is estimated according to the difference between a_ycomp and the product v_xΩ, and then used to solve for bank angle φ_bank. In view of equation (3), a_ycomp can be expressed as:

a _ycomp=(1−gR_gain)a_ym  (12)

where R_gain is the roll gain of vehicle 10 in radians of roll angle per 1 m/sec² of lateral acceleration. The difference d_avΩ between a_ycomp and the product v_xΩ is magnitude limited to a value such as 5 m/sec², and the limited difference d_avΩ—lim is then passed through a low-pass filter with the filter gain b_bf determined at block 46 to determine the bank acceleration ay_bank. The discrete-time form of the low-pass filter equation is given as:

a _ybank(t_i+1)=(1−b_bfΔt)a_ybank(t_i)+b_bfΔtd_avΩ—lim(t_i+1)  (13)

where t_i+1 denotes the current value, t_i denotes a previous value, and Δt is the sampling period. It will be noted that the filter gain term b_bf operates on the limited difference d_avΩ—lim so that the filter is updated quickly during nearly steady-state conditions when b_bf is large (i.e., bfi=1) and slowly during transient maneuvers when b_bf is small (i.e., bfi=0). And once a_ybank is known, the corresponding bank angle estimate φ_ebank is determined according to:

$\begin{array}{cc}{\phi }_{\mathrm{ebank}}={\sin }^{-1}\left(\frac{-a_{\mathrm{ybank}}}{g}\right)& \left(14\right)\end{array}$

Block 50 then determines an estimate φ_erel of relative roll angle φ_rel using the measured lateral acceleration a_ym. In steady-state maneuvers the relative roll angle φ_rel is given by the product (−R_gaina_ym), where R_gain is the roll gain of vehicle 10 in radians of roll angle per 1 m/sec² of lateral acceleration. This relationship is also reasonably accurate during transient maneuvers except in cases where the roll mode of the vehicle is significantly under-damped. In those cases, the roll gain R_gain can be modified by a dynamic second order filter that models the vehicle's roll mode. For example, the filter may be of the form −R_gainb_nf²/(s²+2ζb_nf+b_nf²) where b_nf is the undamped natural frequency of the vehicle's roll mode and ζ is the damping ratio.

Blocks 52 and 54 then determine the total roll angle φ_tot. First, block 52 determines the estimated total roll angle φ_etot according to the sum of the estimated bank angle φ_ebank and the estimated relative roll angle θ_erel. Then block 54 determines a blended estimate φ_ebl of the total roll angle by blending φ_etot with a roll angle determined by integrating the bias-compensated roll rate measurement ω_m—cor. To avoid explicitly integrating ω_m—cor, the terms ω_m—cor, φ_etot and {dot over (φ)}_ebl can be combined with a blending factor b_bl—f in a differential equation as follows:

{dot over (φ)}_ebl+b_bl—fφ_ebl=b_bl—fφ_etot+φ_m—cor  (15)

Representing equation (15) in the Laplace domain, and solving for the blended roll angle estimate φ_ebl yields:

$\begin{array}{cc}{\phi }_{\mathrm{ebl}}=\frac{b_{\mathrm{bl}\_f}}{s+b_{\mathrm{bl}\_f}}{\phi }_{\mathrm{etot}}+\frac{1}{s+b_{\mathrm{bl}\_f}}{\omega }_{m\_\mathrm{cor}}& \left(16\right)\end{array}$

which in practice is calculated on a discrete-time domain basis as follows:

φ_ebl(t_i+1)=(1−b_bl—fΔt)[φ_ebi(t_i)+Δtω_m—cor(t_i+1)]+b_bl—fΔtφ_etot(t_i+1)  (17)

where t_i+1 denotes the current value, t_i denotes a previous value, Δt is the sampling period, and the blending factor b_bl—f is assigned a calibrated value, such as 0.244 rad/sec. If the roll angle obtained by integrating ω_m—cor is denoted by φ_ω, the blended roll angle estimate φ_ebl may be equivalently expressed as:

$\begin{array}{cc}{\phi }_{\mathrm{ebl}}=\frac{b_{\mathrm{bl}\_f}}{s+b_{\mathrm{bl}\_f}}{\phi }_{\mathrm{etot}}+\frac{s}{s+b_{\mathrm{bl}\_f}}{\phi }_{\omega }& \left(18\right)\end{array}$

In this form, it is evident that the blended roll angle estimate φ_ebl is a weighted sum of φ_etot and φ_ω, with the weight dependent on the frequency of the signals (designated by the Laplace operand “s”) so that the blended estimate φ_ebl is always closer to the preliminary estimate that is most reliable at the moment. During steady-state conditions, the body roll rate is near-zero and the signal frequencies are also near-zero. Under such steady-state conditions, the coefficient of φ_etot approaches one and the coefficient of φ_ω approaches zero, with the result that φ_etot principally contributes to φ_ebl. During transient conditions, on the other hand, the body roll rate is significant, and the signal frequencies are high. Under such transient conditions, the coefficient of φ_etot approaches zero and the coefficient of φ_w approaches one, with the result that φ_w principally contributes to φ_ebl.

Block 56 is then executed to compensate the measured lateral acceleration a_ym for the gravity component due to roll angle. The corrected lateral acceleration a_ycor is given by the sum (a_ym+g sin φ_ebl), where φ_ebl is the blended roll angle estimate determined at block 54. The corrected lateral acceleration a_ycor can be used in conjunction with other parameters such as roll rate and vehicle speed for detecting the onset of a rollover event.

Finally, block 58 is executed to use the blended roll angle estimate φ_ebl to estimate other useful parameters including the vehicle side slip (i.e., lateral) velocity v_y and side-slip angle β. The derivative of lateral velocity can alternately be expressed as (a_y−v_xΩ) or (a_ym+g sin φ−v_xΩ), where ay in the expression (a_y−v_xΩ) is the actual lateral acceleration, estimated above as corrected lateral acceleration a_ycor. Thus, the derivative of lateral velocity may be calculated using a_ycor for a_y in the expression (a_y−v_xΩ), or using the blended roll angle estimate φ_ebl for φ in the expression (a_ym+g sin φ−v_xΩ). Integrating either expression then yields a reasonably accurate estimate v_ye of side slip velocity v_y, which can be supplied to block 42 for use in the pitch angle calculation, as indicated by the broken flow line 60. And once the side-slip velocity estimate v_ye has been determined, the side-slip angle β at the vehicle's center of gravity is calculated as:

$\begin{array}{cc}\beta ={\tan }^{-1}\frac{v_{\mathrm{ye}}}{v_x}& \left(19\right)\end{array}$

In summary, the present invention provides a novel and useful way of accurately estimating the absolute roll angle of a vehicle body by blending under any vehicle operating condition. The preliminary roll angle estimates contributing to the blended roll angle are based on typically sensed parameters, including roll rate, lateral acceleration, yaw rate, vehicle speed, and optionally, steering angle and longitudinal acceleration. The preliminary roll angle estimate based on the measured roll rate is improved by initially compensating the roll rate signal for bias error using roll rate estimates inferred from other measured parameters. The other preliminary roll angle estimate is determined according to the sum of the road bank angle and the relative roll angle, with the bank angle being estimated based on the kinematic relationship among lateral acceleration, yaw rate and vehicle speed, and the relative roll angle being estimated based on lateral acceleration and the roll gain of the vehicle. The blended estimate of roll angle utilizes a blending factor that varies with the frequency of the preliminary roll angle signals so that the blended estimate continuously favors the more accurate of the preliminary roll angle estimates. The blended estimate is used to estimate the actual lateral acceleration, the lateral velocity and side-slip angle of the vehicle, all of which are useful in applications such as rollover detection and vehicle stability control.

While the present invention has been described with respect to the illustrated embodiment, it is recognized that numerous modifications and variations in addition to those mentioned herein will occur to those skilled in the art. For example, the preliminary estimate of relative roll angle φ_rel may be obtained from suspension deflection sensors instead of equation (3) if such sensors are available. Also, the lateral velocity may be determined using a model-based (i.e., observer) technique with the corrected lateral acceleration a_ycor as an input, instead of integrating the estimated derivative of lateral velocity. Finally, it is also possible to apply the blending method of this invention to estimation of absolute pitch angle θ in systems including a pitch rate sensor; in that case, a first preliminary pitch angle estimate would be obtained by integrating a bias-compensated measure of the pitch rate, and a second preliminary pitch angle estimate would be obtained from equation (8). Of course, other modifications and variations are also possible. Accordingly, it is intended that the invention not be limited to the disclosed embodiment, but that it have the full scope permitted by the language of the following claims.

Claims

1. A method of operation for a vehicle having a body that rolls about a longitudinal axis relative to a level ground plane, comprising the steps of: determining a first preliminary estimate of a total roll angle of the vehicle body based on a signal produced by a roll rate sensor, said first preliminary estimate having an accuracy that is highest under transient conditions when a roll rate of the vehicle body is relatively high;determining a second preliminary estimate of the total roll angle based on a sum of an estimated bank angle of a road surface supporting the vehicle with respect to the level ground plane and an estimated relative roll angle of the vehicle body with respect to the road surface, said second preliminary estimate having an accuracy that is highest under near steady-state conditions when the roll rate of the vehicle body is relatively low;blending the first and second preliminary estimates of the total roll angle with blending coefficients to form a blended estimate of the total roll angle, where the blending coefficients are continuously variable according to a frequency of said first and second preliminary estimates so that the blended estimate favors the first preliminary estimate under the transient conditions and the second preliminary estimate under the near steady-state conditions; andcontrolling a vehicle system based on the blended estimate of the total roll angle.

2. The method of claim 1, including the steps of: determining a bias error in the signal produced by the roll rate sensor; andremoving the determined bias error from the signal produced by the roll rate sensor before determining said first preliminary estimate of the total roll angle.

3. The method of claim 2, where the step of determining the bias error in the signal produced by the roll rate sensor includes the steps of: determining at least one auxiliary roll rate estimate based on sensed parameters other than the roll rate during the steady-state conditions;determining a difference between the auxiliary roll rate estimate and the signal produced by the roll rate sensor;limiting a magnitude of said difference to form a limited difference; anddetermining said bias error by low-pass filtering said limited difference.

4. The method of claim 3, where the step of determining at least one auxiliary roll rate estimate includes the steps of: determining a roll angle estimate based on sensed parameters other than the roll rate during the steady-state conditions; anddifferentiating the determined roll angle estimate to form the auxiliary roll rate estimate.

5. The method of claim 1, including the steps of: measuring a lateral acceleration of said vehicle body; anddetermining the estimated relative roll angle of the vehicle body based on a product of the measured a lateral acceleration and a known roll gain of the vehicle.

6. The method of claim 1, including the steps of: measuring a lateral acceleration and a yaw rate of said vehicle body;estimating a longitudinal velocity of said vehicle; andusing the measured lateral acceleration and yaw rate and the estimated longitudinal velocity to determine a bank component of the measured lateral acceleration that is due to the bank angle; andestimating the bank angle based on the determined bank component of the measured lateral acceleration.

7. The method of claim 6, including the steps of: compensating the measured lateral acceleration for effects of the relative roll angle;determining a difference between the compensated measured lateral acceleration and a product of the measured yaw rate and the estimated longitudinal velocity;limiting a magnitude of said difference to form a limited difference; andpassing said limited difference through a low-pass filter to determine said bank component.

8. The method of claim 7, where said low-pass filter has a gain term that determines a rate at which said limited difference passes through said low pass filter, and the method includes the step of: setting said gain term to a first value for passing said limited difference through said low pass filter at a high rate when a yaw motion of the vehicle body is relatively low, and otherwise setting said gain term to a second value for passing said limited difference through said low pass filter at a low rate.

9. The method of claim 1, including the steps of: measuring a lateral acceleration of the vehicle body; andcompensating the measured lateral acceleration for a gravity component due to the blended estimate of the total roll angle; andcontrolling the vehicle system based on compensated lateral acceleration.

10. The method of claim 1, including the steps of: determining a lateral velocity of the vehicle body based on the blended estimate of the total roll angle; andcontrolling the vehicle system based on determined lateral velocity.

11. The method of claim 10, including the steps of: determining a pitch angle of the vehicle body based on the determined lateral velocity, measures of longitudinal acceleration and yaw rate of the vehicle body, and an estimated longitudinal velocity of the vehicle;compensating the signal produced by the roll rate sensor due to the determined pitch angle; anddetermining said first preliminary estimate of the total roll angle based on the compensated roll rate sensor signal.

12. The method of claim 10, including the step of: determining a side-slip angle of the vehicle based on the determined lateral velocity and an estimate of a longitudinal velocity of the vehicle; andcontrolling the vehicle system based on determined side-slip angle.