US20060204347A1 - Method and device for stabilizing a vehicle combination - Google Patents

Method and device for stabilizing a vehicle combination Download PDF

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US20060204347A1
US20060204347A1 US10/534,096 US53409603A US2006204347A1 US 20060204347 A1 US20060204347 A1 US 20060204347A1 US 53409603 A US53409603 A US 53409603A US 2006204347 A1 US2006204347 A1 US 2006204347A1
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Prior art keywords
differential value
frequency
threshold value
value
driving
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US10/534,096
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Dirk Waldbauer
Jurgen Krober
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Continental Teves AG and Co OHG
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Continental Teves AG and Co OHG
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Assigned to CONTINENTAL TEVES AG & CO., OHG reassignment CONTINENTAL TEVES AG & CO., OHG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KROBER, JURGEN, WALDBAUER, DIRK
Publication of US20060204347A1 publication Critical patent/US20060204347A1/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/24—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to vehicle inclination or change of direction, e.g. negotiating bends
    • B60T8/248—Trailer sway, e.g. for preventing jackknifing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T7/00—Brake-action initiating means
    • B60T7/12—Brake-action initiating means for automatic initiation; for initiation not subject to will of driver or passenger
    • B60T7/20—Brake-action initiating means for automatic initiation; for initiation not subject to will of driver or passenger specially for trailers, e.g. in case of uncoupling of or overrunning by trailer
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/17—Using electrical or electronic regulation means to control braking
    • B60T8/1701—Braking or traction control means specially adapted for particular types of vehicles
    • B60T8/1708—Braking or traction control means specially adapted for particular types of vehicles for lorries or tractor-trailer combinations
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/17—Using electrical or electronic regulation means to control braking
    • B60T8/1755—Brake regulation specially adapted to control the stability of the vehicle, e.g. taking into account yaw rate or transverse acceleration in a curve
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T2230/00—Monitoring, detecting special vehicle behaviour; Counteracting thereof
    • B60T2230/06—Tractor-trailer swaying

Definitions

  • the present invention relates to a method and a device for stabilizing a car-trailer combination, including a towing vehicle and a trailer moved by the towing vehicle, wherein the towing vehicle is monitored in terms of rolling motions and measures that stabilize driving are taken upon the detection of an actual or expected unstable driving performance of the towing vehicle or the car-trailer combination.
  • the present method aims at detecting and controlling the instabilities of car-trailer combinations (motor vehicle with trailer), especially of combinations consisting of a passenger car, pickup truck or sport-utility vehicle and any trailers desired, in particular caravans, before driving conditions are encountered during which the driver can no longer maintain control of the vehicle.
  • These unstable conditions involve the rolling motions known with car-trailer combinations and the anti-phase build-up process between the towing vehicle and the trailer as well as imminent roll-over conditions at too high lateral accelerations caused by obstacle avoidance maneuvers, lane changes, side wind, road irregularities and/or hasty steering maneuver requests by the driver.
  • the oscillations can decay, remain constant, or increase (undamped oscillation).
  • the car-trailer combination has reached the critical velocity. Above this speed threshold a car-trailer combination is unstable, below said threshold it is stable, that means, possible oscillations die out.
  • this critical speed depends on the geometry data, the tire rigidities, the weight and the distribution of weight of the towing vehicle and the trailer. Further, the critical speed is lower in a braked driving maneuver than at constant travel. In turn, it is higher during accelerated driving than at constant travel.
  • DE 197 42 707 C2 discloses a device for damping rolling motions for at least one trailer towed by a towing vehicle, wherein the angular velocity of the trailer about the instantaneous center of rotation or the articulated angle about the instantaneous center of rotation is sensed and differentiated and taken into consideration for controlling the wheel brakes of the trailer. Acceleration sensors at different locations are used as sensors for the angular velocity.
  • DE 199 64 048 A1 also provides a lateral acceleration sensor or a yaw rate sensor by means of which the rolling motion is determined. After the signal is evaluated, a periodic yawing torque shall be applied to the vehicle.
  • DE 100 34 222 A1 determines a time for a braking intervention correct in phase, being realized in dependence on the quantity of frequency and the phase magnitude of the rolling motion.
  • the detection of the rolling motion of a car-trailer combination is mainly based on the fact that the yaw rate or lateral acceleration shows an almost sinusoidal variation, the frequency of which lies in a typical band, without the driver performing corresponding steering movements that would cause the observed variation of lateral quantities. It is problematic with this detection strategy that there are still other maneuvers generating similar variations of signals. Thus, sprung-mass vibrations may be produced, e.g. during cornering with a constant steering angle, which also induce sinusoidal variations of lateral quantities. Another possibility of obtaining such variations of lateral quantities is to drive over rough roadways, in particular wavy road sections, especially bumps on alternating sides.
  • An object of the invention is to provide a method and a device permitting the reliable detection of unstable driving performance.
  • this object is achieved in that the yaw velocity is detected and measures that stabilize driving are controlled dependent on a differential value that is produced from the detected yaw velocity and a model-based yaw velocity and evaluated according to criteria indicative of an unstable driving performance.
  • the method allows for reliably detecting snaking car-trailer combinations, in particular passenger car/trailer combinations.
  • a differential value ⁇ dot over ( ⁇ ) ⁇ is generated from the measured yaw rate and the model-based reference yaw rate, which value is representative of the deviation of the vehicle from the track predetermined by the steering wheel position. Because this differential value represents only the deviation from the desired track, monitoring the differential value ensures the judgment of oscillations independently of a curved track passed e.g. due to a steering angle.
  • the differential value is filtered in a low-pass filter in order to cut off signal peaks triggered by the detection of coefficients of friction. Spurious detections and, thus, faulty control activations are avoided in addition.
  • the method and the device favorably require only a sensor system provided in an Electronic Stability Program (ESP) driving stability control.
  • ESP Electronic Stability Program
  • an actuating signal for an electric motor of a hydraulic pump producing a brake pressure and, hence, actuating the wheel brake of the towing vehicle or the trailer is generated by way of the data measured by a yaw rate sensor, derived in an ESP driving dynamics control operation and logically combined with the ESP control strategy.
  • the data of a motor vehicle can be included. It is possible alternatively or additionally to drive an actuator of an overriding steering system.
  • the oscillation frequency of the car-trailer combination is achieved in that the frequency is determined from the zero crossings and the time between two zero crossings of the yaw velocity.
  • the condition for detecting a snaking, unstable car-trailer combination is favorably satisfied by the following steps: counting the number of the half waves of the differential value where the amplitude of each half wave reaches or exceeds a threshold value, counting each positive and negative half wave of the determined frequency when each positive and negative half wave lies within a band defined by a top and a bottom threshold value, and comparing the value of the half waves counted with a threshold value representative of a number of half waves, and measures that stabilize driving are initiated when the threshold value is reached or exceeded. It is favorably arranged so that the conditions are continuously satisfied and the half waves are serially counted in order that the threshold value representative of a number of half waves is reached or exceeded, respectively.
  • the threshold value representative of a number of half waves can favorably be determined in dependence on the frequency, and at low frequencies, the threshold value is reached or exceeded with a smaller number of half waves than is the case at a high frequency.
  • the threshold value of each half wave representative of the amplitude is determined at least in dependence on quantities that represent the velocity of the towing vehicle or the car-trailer combination or the trailer. It is arranged for that with quantities describing a high speed, the threshold value is reached or exceeded at lower amplitudes than is the case with quantities describing a low speed.
  • ESP driving stability controller To avoid constant activation and deactivation of the controller (ESP driving stability controller), only a consecutive number of half waves of the yaw velocity are counted where the amplitude of each half wave reaches or exceeds an entry threshold value, and the measures that stabilize driving are terminated when values reach or fall below only one exit threshold value ranging below the entry threshold value.
  • the data is produced from the variation of the differential value.
  • the model-based yaw velocity is calculated in a vehicle model that is a component of an ESP driving stability control in a favorable manner.
  • the model yaw rate is generally produced from the steering angle, the lateral acceleration and the vehicle speed (vehicle reference speed).
  • the lateral acceleration is detected and the variation of the lateral acceleration is evaluated according to criteria which allow checking the plausibility of the data obtained from the variation of the differential value and being assessed according to criteria indicative of an unstable driving performance.
  • Plausibility is checked by way of finding out the maximum and minimum values of the lateral acceleration and their temporal distances, by determining the frequency and comparing it with the frequency of the differential value.
  • phase shift is small in snaking car-trailer combinations, it is favorably arranged so that the phase shift between the lateral acceleration and the differential value is determined and evaluated according to criteria that permit determining driving situations.
  • an object of the invention relates to a device for stabilizing a car-trailer combination, including an ESP driving stability control, with a yaw rate sensor for sensing the yaw velocity and a vehicle model for producing a reference yaw velocity, with a determining unit determining a differential value from the yaw velocity and the reference yaw velocity, with a control unit controlling measures that stabilize driving in dependence on data being obtained from the variation of the differential value and evaluated according to criteria indicative of an unstable driving performance.
  • an ESP driving stability control with a yaw rate sensor for sensing the yaw velocity and a vehicle model for producing a reference yaw velocity, with a determining unit determining a differential value from the yaw velocity and the reference yaw velocity, with a control unit controlling measures that stabilize driving in dependence on data being obtained from the variation of the differential value and evaluated according to criteria indicative of an unstable driving performance.
  • FIG. 1 shows a vehicle with an ESP control system.
  • FIG. 2 shows the variation of signals of the differential value of the snaking towing vehicle.
  • FIG. 3 shows the signals of a snaking towing vehicle.
  • FIG. 4 is a simplified flow chart showing the control.
  • FIG. 5 is a simplified wiring diagram for calculating the differential value ⁇ dot over ( ⁇ ) ⁇ .
  • FIG. 3 shall be used to schematically explain the signal variation of the oscillation of the yaw rate (dash-dot), of the steering angle (dash-dash), and the differential value of measured yaw rate and model or reference yaw rate in dependence on a slalom maneuver or the slalom-like avoidance of obstacles, respectively.
  • the signal variation a) shows a sinusoidal variation of the yaw rate ⁇ dot over ( ⁇ ) ⁇ and the differential value ⁇ dot over ( ⁇ ) ⁇ of model yaw rate and measured yaw rate without the driver steering. Without a corresponding steering angle variation, the variation of the yaw rate and the differential value of measured yaw rate and model-based yaw rate are almost equal.
  • FIG. 3 b shows the signal variation that is e.g. produced in a slalom maneuver when the oscillation is generated by the steering angle variation alone, where the vehicle can follow the driving performance of the driver illustrated in the vehicle model.
  • the differential value at issue is zero because no deviation between measured yaw rate and model-based yaw rate is determined.
  • the vehicle follows the steering angle predefined by the driver.
  • FIG. 3 c shows the signal variation in dynamic slalom maneuvers.
  • the oscillation is generated alone by the steering angle variation due to the rapid steering angle changes, i.e. at high steering angle velocities.
  • the sinusoidal variation of the differential value is generally based on the fact that the vehicle can no longer follow the vehicle model. That means, the model yaw rate determined in the vehicle model is no longer identical with the measured yaw rate because the vehicle is no longer able to instantaneously comply with the dynamic steering angle variations.
  • FIG. 1 shows a vehicle with an ESP control system, brake system, sensor system, and communication provisions.
  • the four wheels have been assigned reference numerals 15 , 16 , 20 , 21 .
  • One wheel sensor 22 , 23 , 24 , 25 is provided at each of the wheels 15 , 16 , 20 , 21 .
  • the signals are sent to an electronic control unit 28 determining from the wheel rotational speeds the vehicle speed v by way of predetermined criteria.
  • a yaw rate sensor 26 , a lateral acceleration sensor 27 , and a steering angle sensor 29 are connected to the electronic control unit 28 .
  • each wheel includes an individually actuatable wheel brake 30 , 31 , 32 , 33 .
  • the brakes are hydraulically operated and receive pressurized hydraulic fluid by way of hydraulic lines 34 , 35 , 36 , 37 .
  • the brake pressure is adjusted by way of a valve block 38 , said valve block being actuated irrespective of the driver by way of electric signals produced in the electronic control unit 28 .
  • the driver can introduce brake pressure into the hydraulic lines by way of a master cylinder actuated by a brake pedal.
  • Pressure sensors P are used to sense the driver's braking request are provided in the master cylinder or the hydraulic lines, respectively.
  • the electronic control unit is connected to the engine control device by way of an interface (CAN).
  • a conventional ESP intervention is used to produce an additional torque by purposeful interventions at the individual brakes of a vehicle, said torque adapting the actually measured yaw angle variation per unit of time (actual yaw rate ⁇ dot over ( ⁇ ) ⁇ actual ) of a vehicle to the yaw angle variation per unit of time (reference or model or nominal yaw rate ⁇ dot over ( ⁇ ) ⁇ no min al , respectively) influenced by the driver.
  • the input quantities which result from the track desired by the driver are sent to a vehicle model circuit which, by way of the prior-art single track model or any other driving model, determines a model yaw rate ( ⁇ dot over ( ⁇ ) ⁇ no min al ) from these input quantities and from parameters being characteristic of the driving performance of the vehicle, but also from quantities predefined by distinctive features of the ambience.
  • Said model yaw rate is compared to the measured actual yaw rate ( ⁇ dot over ( ⁇ ) ⁇ actual ).
  • the difference between the model yaw rate and the actual yaw rate ( ⁇ dot over ( ⁇ ) ⁇ ) is converted by means of a so-called yaw torque controller into an additional yaw torque M G which represents the input quantity of a distribution logic.
  • Distribution logic determines the brake pressure to be applied to the individual brakes, possibly in dependence on a braking request of the driver demanding a defined brake pressure at the wheel brakes.
  • the purpose of the brake pressure is to produce an additional torque at the vehicle in addition to the desired brake effect, as the case may be, said torque supporting the driving performance of the vehicle in the direction of the steering request of the driver.
  • FIG. 5 schematically shows that part of the ECU 28 wherein the differential value ⁇ dot over ( ⁇ ) ⁇ is calculated.
  • ECU 28 includes a vehicle model 50 for producing a model yaw rate. At least the steering angle and the vehicle speed vRef are sent to the vehicle model 50 . Further data, which can be included in the model, are the lateral acceleration, the measured yaw rate and a coefficient of friction determined in a coefficient-of-friction and situation detection unit. The model yaw rate is produced from the input signals in the model.
  • the model yaw rate is compared with the yaw rate sensed by the yaw rate sensor 26 , and the differential value is determined from the yaw rate and the model yaw rate.
  • the differential value ⁇ dot over ( ⁇ ) ⁇ /dt is weighted by a factor produced in dependence on the model yaw rate change and is filtered in filter 52 .
  • the factor ⁇ 0 prevents the spurious detection that has been described with respect to FIG. 3 c ).
  • FIG. 2 exhibits the signal variation of the differential value of a snaking towing vehicle.
  • the method comprises a module for analyzing the variation of the difference of the model/actual yaw rate ⁇ dot over ( ⁇ ) ⁇ .
  • the model detects zero crossings 60 , 61 of the differential value between the model yaw rate and the measured yaw rate, said differential value to be taken into account for the analysis, and determines the time between two zero crossings.
  • the oscillation frequency is thereby obtained.
  • a half wave is recognized as valid only if the determined frequency lies within a typical band (roughly 0.5-1.5 hertz). Further, a half wave is valid only if the amplitude between two zero crossings has exceeded a defined threshold. The number of the valid half waves is counted. When the number of the valid half waves exceeds a threshold value, the differential value condition for detecting a snaking car-trailer combination is satisfied.
  • Steering movements of the driver are considered directly in the detection signal by way of monitoring the difference between the model yaw rate and the measured yaw rate.
  • the driver e.g. carries out a slalom maneuver at a low vehicle speed with a low steering angle velocity
  • the measured yaw rate shows a variation from which a snaking car-trailer combination could be concluded.
  • the model yaw rate shows the same variation in the slalom maneuver so that the difference signal is almost zero and a spurious detection is ruled out.
  • spurious detections caused by slalom maneuvers are thus avoided due to this embodiment of the method.
  • this method simplifies detecting snaking car-trailer combinations in a curve.
  • the yaw rate is given an offset so that the oscillation no longer swings about the zero point but about this offset. This fact renders detection more difficult. If, however, the difference between the model yaw rate and the measured yaw rate (yaw velocity) is used, this offset will be compensated. The detection signal will thus always swing about zero.
  • Another especially favorable embodiment of the method provides that the deviation between actual yaw rate and model yaw rate is additionally weighted by a factor that is calculated in response to the model yaw rate speed.
  • Said factor is multiplied by the differential value or differential value signal so that a low differential value is the result in the event of a quick change of the model yaw rate.
  • detection is only allowed in the presence of extreme oscillations, but is avoided in other cases. It is thereby taken into account that with rapid steering movements the vehicle is no longer able to follow the vehicle model so that the difference between the model yaw rate and the measured yaw rate shows a signal variation that would cause spurious detections.
  • the number of the demanded half waves depends on the frequency of the oscillation. The more half waves are demanded, the more reliable the detection of spurious detections becomes. With low frequencies, however, it will possibly last too long until an intervention can take place when great numbers of half waves are demanded. It is, therefore, favorable to intervene already at low frequencies when small numbers of half waves prevail, yet to demand more half waves at high frequencies.
  • the demanded oscillation amplitudes are speed-responsive. Oscillations are more critical at high speeds than at low speeds. Therefore, detection takes place already at low differential value oscillations when the car-trailer combination runs at high speed, while the threshold is raised at low speeds.
  • the method comprises a module for analyzing the lateral acceleration variation.
  • Maximums and minimums of the signal are determined.
  • the frequency can be determined from the distances in time between maximums and minimums. The frequency must roughly correspond to the frequency of the differential value signal.
  • the position of the maximums and minimums of the lateral acceleration signal is compared with the position of the maximums and minimums of the differential value signal.
  • the phase shift between differential value and lateral acceleration can be calculated therefrom.
  • the phase position during driving on rough roadways is different from the phase position during driving with snaking car-trailer combinations.
  • the phase shift is small with snaking car-trailer combinations. This criterion is examined, and the detection of a snaking car-trailer combination is forbidden in the event of a too great phase shift.
  • spurious control activations are prevented by way of several additional plausibility tests of the lateral signals.
  • the following signal variations are untypical with snaking car-trailer combinations and, therefore, cause prevention or stop of interventions:
  • FIG. 4 shows a simplified view of the logical processes of the control:
  • Step 40 comprises the search for half waves in the input signal, which are analyzed by way of two zero crossings, one maximum, a minimum amplitude and a defined initial gradient. It is polled in lozenge 43 whether the half wave was detected.
  • step 42 If this is not the case, switch-back to step 42 is made and the search for half waves is continued. If the half wave was detected by way of the previous criteria, it is checked in terms of its validity in lozenge 44 . To this end, the following criteria are polled:
  • the half wave counter is incremented in step 45 .
  • the counter will not be incremented but maintains its value, what can lead to a later entry into the control. If not all the criteria are satisfied, the half wave counter is reset to zero in step 48 . It is found out in lozenge 46 whether N half waves are detected. This will trigger a deceleration control of the vehicle in step 47 .
  • the criteria allow a control during cornering and even during steering movements of the driver.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)
  • Control Of Driving Devices And Active Controlling Of Vehicle (AREA)
US10/534,096 2002-11-08 2003-11-07 Method and device for stabilizing a vehicle combination Abandoned US20060204347A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10252510 2002-11-08
DE10252510.2 2002-11-08
PCT/EP2003/050802 WO2004041612A1 (de) 2002-11-08 2003-11-07 Verfahren und einrichtung zum stabilisieren eines gespanns

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US (1) US20060204347A1 (de)
EP (1) EP1562811B1 (de)
JP (1) JP4758102B2 (de)
DE (2) DE10393558D2 (de)
WO (1) WO2004041612A1 (de)

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EP1562811B1 (de) 2011-01-12
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