Abstract: A press-formed product includes a body having a transverse cross section including a bottom portion and a shoulder portion contiguous to the bottom portion through an R end. In the transverse cross section, a first region from the R end to a position a distance away in a bottom portion extending direction, and a second region which is part of the bottom portion and is contiguous to the first region have a work-hardening distribution introduced by press-forming. The work-hardening distribution has an average hardness Hv1 of an area of the first region from a steel sheet surface to a depth obtained by multiplying a steel sheet thickness by 0.2 and an average hardness Hv2 of an area of the second region from the steel sheet surface to a position obtained by multiplying the steel sheet thickness by 0.2 to satisfy a relationship of Hv1>1.05×Hv2.

Abstract: A vehicle motion control apparatus configured to be used with a vehicle including a brake force control unit capable of generating a brake force during a steering operation. The control apparatus includes a plurality of force generation apparatuses disposed between a vehicle body of the vehicle and a plurality of axles, each of which is capable of generating an adjustable force between the vehicle body and each wheel of the vehicle, a force adjustment unit configured to adjust the force of each of the force generation apparatuses, and a target pitch state calculation unit configured to calculate a target pitch state from a state in which the vehicle body turns. The force adjustment unit adjusts the force of each of the force generation apparatuses so that a pitch state of the vehicle body approaches the target pitch state calculated by the target pitch state calculation unit.

Abstract: A vehicle body attitude control apparatus capable improving cornering operability, steering stability, and ride comfort while a vehicle is running. A controller includes a gain, a determination unit, a multiplication unit, an FF control unit, a difference calculation unit, an FB control unit, an average value calculation unit, a target damping force calculation unit, and a damper instruction value calculation unit so as to enable such control that a pitch rate and a roll rate are set into a proportional relationship while the vehicle is cornering. The controller calculates a target pitch rate proportional to the roll rate, variably controls a damping force characteristic of a damping force variable damper disposed at each the wheels so as to achieve the target pitch rate, and generates a pitch moment to be applied to the vehicle body.

Abstract: A suspension control apparatus enabling a driver to obtain an excellent driving feeling. The suspension control apparatus controls an actuator disposed between a vehicle body and a wheel of a vehicle. The suspension control apparatus includes a lateral acceleration detector operable to detect a lateral acceleration, a lateral jerk detector operable to detect a lateral jerk, and a suspension controller operable to control the actuator to change a pitch of the vehicle based the detected lateral acceleration and lateral jerk.

Abstract: Shock absorbers of left and right front wheel suspensions and shock absorbers of left and right rear wheel suspensions each are constituted by a damping force adjustable hydraulic shock absorber provided with a frequency response unit. An actuator of a damping force variable mechanism provided to the shock absorber is driven and controlled by a controller. The controller variably adjusts the damping force between the soft side and the hard side by the damping force variable mechanism according to a vertical vibration when a vehicle body vertically vibrates at a low frequency. The controller does not adjust the damping force when the vehicle body vibrates at a higher frequency than the low frequency.

Abstract: A first observer gain of an actual damping force estimating observer 21 calculates a dynamic characteristic compensating signal, and a second observer gain of an actual vehicle model state amount estimating observer 23 calculates a vehicle model compensating signal, from an output deviation corresponding to a difference between a sprung speed (observation output) provided from a vehicle 2 and an estimated sprung speed (estimated observation output) provided from a vehicle approximation model of the actual vehicle model state amount estimating observer 23. The dynamic characteristic compensating signal is input into a dynamic characteristic providing unit of the actual vehicle model state amount estimating observer 23, and is used for adjustment of the setting of the dynamic characteristic providing unit. Therefore, it is possible to curb time lag occurrence in a control, and thereby perform a vibration control with improved accuracy.

Abstract: The present invention provides a vehicle body attitude control apparatus capable of improvement of cornering operability, steering stability, and a ride comfort while a vehicle is running. A controller includes a gain, a determination unit, a multiplication unit, an FF control unit, a difference calculation unit, an FB control unit, an average value calculation unit, a target damping force calculation unit, and a damper instruction value calculation unit so as to enable such control that a pitch rate and a roll rate are set into a proportional relationship while the vehicle is cornering. The controller calculates a target pitch rate proportional to the roll rate, variably controls a damping force characteristic of a damping force variable damper disposed at each of front left, front right, rear left, and rear right wheels so as to achieve the target pitch rate, and generates a pitch moment to be applied to the vehicle body accordingly.

Abstract: A collision between a vehicle and an obstacle is estimated, and based on the estimation result, vehicle deceleration control is performed by a brake actuator to reduce the collision and vehicle wheel load is controlled by a suspension actuator.

Abstract: The present invention provides a suspension control apparatus capable of an excellent vibration control by a model thereof designed to incorporate nonlinearity and a time-lag element of a control damper. The present invention employs the backstepping method which is one of nonlinear control methods, and is designed so as to incorporate the nonlinearity of a damper 4. In addition, a nonlinear controller 5 uses a damping force Fu obtained by expressing the dynamics of a damping force characteristic variable portion [damping force Fu(v, i)] by a first-order lag system, so as to compensate the dynamics of the damper 4, whereby a control system is formed so as to incorporate the time-lag element of the control damper. As a result, it is possible to reduce time lag, and to practically adjust a control force according to the characteristics of the control damper.

Abstract: Provided is a suspension control apparatus for a vehicle comprising a damping-force adjustable shock absorber interposed between a vehicle body and a wheel of a vehicle, and a controller for variably controlling damping-force characteristics of the damping-force adjustable shock absorber between hard and soft, wherein the controller is configured to switch the damping-force characteristics to a soft side when a direction of a stroke of the damping-force adjustable shock absorber is reversed between an extension stroke and a contraction stroke.

Abstract: The present invention provides a suspension control apparatus enabling a driver to obtain an excellent driving feeling. A suspension control apparatus according to the present invention controls an actuator disposed between a vehicle body and a wheel of a vehicle. The suspension control apparatus comprises a lateral acceleration detector operable to detect a lateral acceleration, a lateral jerk detector operable to detect a lateral jerk, and a suspension controller operable to control the actuator to change a pitch of the vehicle based the detected lateral acceleration and lateral jerk.

Abstract: A first observer gain of an actual damping force estimating observer 21 calculates a dynamic characteristic compensating signal, and a second observer gain of an actual vehicle model state amount estimating observer 23 calculates a vehicle model compensating signal, from an output deviation corresponding to a difference between a sprung speed (observation output) provided from a vehicle 2 and an estimated sprung speed (estimated observation output) provided from a vehicle approximation model of the actual vehicle model state amount estimating observer 23. The dynamic characteristic compensating signal is input into a dynamic characteristic providing unit of the actual vehicle model state amount estimating observer 23, and is used for adjustment of the setting of the dynamic characteristic providing unit. Therefore, it is possible to curb time lag occurrence in a control, and thereby perform a vibration control with improved accuracy.

Abstract: The present invention provides a suspension control apparatus capable of an excellent vibration control by a model thereof designed to incorporate nonlinearity and a time-lag element of a control damper. The present invention employs the backstepping method which is one of nonlinear control methods, and is designed so as to incorporate the nonlinearity of a damper 4. In addition, a nonlinear controller 5 uses a damping force Fu obtained by expressing the dynamics of a damping force characteristic variable portion [damping force Fu(v, i)] by a first-order lag system, so as to compensate the dynamics of the damper 4, whereby a control system is formed so as to incorporate the time-lag element of the control damper. As a result, it is possible to reduce time lag, and to practically adjust a control force according to the characteristics of the control damper.

Abstract: In a suspension control system a sky-hook command signal (B) obtained from velocity data obtained by integrating a sprung mass acceleration (?u) from a sprung mass acceleration sensor (9u) and an unsprung mass vibration damping command signal (C) obtained on the basis of an unsprung mass acceleration (?d) detected by an unsprung mass acceleration sensor (9d) are added together to obtain a control signal (A) for a damping characteristic inverting type shock absorber (6). The control signal (A) reflects the unsprung mass acceleration (?d) that leads in phase by 90° the piston speed. Accordingly, it is possible to compensate for a response delay due to an actuator (11), etc.

Abstract: The piston 10 is constituted so as to rotate relative to the first cylinder 8 while moving relative to the first cylinder 8 in the axial direction when fluid is supplied to and discharged from the interior of the first cylinder 8, and the piston 16 is constituted to be incapable of rotation relative to the second cylinder 9, but capable of movement relative to the second cylinder 9 in the axial direction. Hence when fluid is supplied to and discharged from the interior of the first cylinder 8, the piston 10 is caused to rotate relative to the first cylinder 8 while moving relative to the first cylinder 8 in the axial direction, and the piston 16 is caused to move relative to the second cylinder 9 in the axial direction but prevented from rotating relative to the second cylinder 9. As a result, torsional elasticity is generated in shaft portions 4a and 5a.

Abstract: A collision between a vehicle and an obstacle is estimated, and based on the estimation result, vehicle deceleration control is performed by a brake actuator to reduce the collision and vehicle wheel load is controlled by a suspension actuator.

Abstract: In a suspension control system according to the present invention, a sky-hook command signal B obtained from velocity data obtained by integrating a sprung mass acceleration ?u from a sprung mass acceleration sensor 9u and an unsprung mass vibration damping command signal C obtained on the basis of an unsprung mass acceleration ?d detected by an unsprung mass acceleration sensor 9d are added together to obtain a control signal A for a damping characteristic inverting type shock absorber 6. The control signal A reflects the unsprung mass acceleration ?d that leads in phase by 90° the piston speed. Accordingly, it is possible to compensate for a response delay due to an actuator 11, etc.

Abstract: The piston 10 is constituted so as to rotate relative to the first cylinder 8 while moving relative to the first cylinder 8 in the axial direction when fluid is supplied to and discharged from the interior of the first cylinder 8, and the piston 16 is constituted to be incapable of rotation relative to the second cylinder 9, but capable of movement relative to the second cylinder 9 in the axial direction. Hence when fluid is supplied to and discharged from the interior of the first cylinder 8, the piston 10 is caused to rotate relative to the first cylinder 8 while moving relative to the first cylinder 8 in the axial direction, and the piston 16 is caused to move relative to the second cylinder 9 in the axial direction but prevented from rotating relative to the second cylinder 9. As a result, torsional elasticity is generated in shaft portions 4a and 5a.

Abstract: In a suspension control system, a controller previously stores damping force maps (an ordinary road map, a rough road map, and an extremely rough road map) corresponding to road surface conditions (an ordinary road, a rough road, and an extremely rough road) defined by frequency and amplitude of vertical acceleration. The frequency and amplitude of the vertical acceleration are detected, and a damping force map (the ordinary road map, the rough road map, or the extremely rough road map) corresponding to the detected information is selected. Damping force control is effected on the basis of the selected damping force map. Selection of a damping force map according to the frequency and amplitude of the vertical acceleration is also made when a change in the vertical acceleration, i.e. a change in piston speed, is predicted during running on an ordinary road, a rough road or an extremely rough road.

Abstract: By passing the vertical acceleration through a phase adjusting filter and a gain adjusting filter, the phase of the vertical acceleration is advanced by 49 degrees so that the phase difference with respect to the actual relative velocity becomes 180 degrees in the neighborhood of the vehicle body resonance point, thereby making the phase of the vertical acceleration, in effect, coincident with the phase of the relative velocity. In the neighborhood of the vehicle body resonance point (1 Hz), the gain of the estimated relative velocity takes a small value. In frequency regions other than the neighborhood of the vehicle body resonance point, the gain of the estimated relative velocity is increased. Consequently, the controlled variable in the neighborhood of the vehicle body resonance point increases, and the controlled variable in higher frequency regions decreases. Damping force is adjusted in correspondence to the controlled variable.