JPH03112757A - Turn action control device for vehicle - Google Patents
Turn action control device for vehicleInfo
- Publication number
- JPH03112757A JPH03112757A JP25064689A JP25064689A JPH03112757A JP H03112757 A JPH03112757 A JP H03112757A JP 25064689 A JP25064689 A JP 25064689A JP 25064689 A JP25064689 A JP 25064689A JP H03112757 A JPH03112757 A JP H03112757A
- Authority
- JP
- Japan
- Prior art keywords
- vehicle
- turning
- wheel
- brake pedal
- turn
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000028838 turning behavior Effects 0.000 claims description 18
- 238000001514 detection method Methods 0.000 claims description 9
- 230000000994 depressogenic effect Effects 0.000 claims description 6
- 230000004044 response Effects 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 6
- 230000000881 depressing effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000009286 beneficial effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000006399 behavior Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
Landscapes
- Regulating Braking Force (AREA)
- Hydraulic Control Valves For Brake Systems (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明は車両の旋回挙動、特に運転者が高速旋回のため
ブレーキペダルを踏込みながらアクセルペダルをも踏込
む所謂ヒール・アンド・トー操作を行う時の旋回挙動を
制御する装置に関するものである。[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to the turning behavior of a vehicle, particularly the so-called heel-and-toe operation in which the driver depresses the accelerator pedal while depressing the brake pedal in order to make a high-speed turn. The present invention relates to a device that controls turning behavior during rotation.
(従来の技術)
アンダーステア傾向の車両にあっては特に、高速で湾曲
路に突入した場合、走行軌跡が旋回方向外側へふくらむ
傾向にあり、これを防止するため運転者はステアリング
ホイールを切増ししたり、それでも足りなければブレー
キペダルの踏込みにより車両を制動して荷重移動を惹起
せしめ、これにともなう前輪荷重の増大で前輪のコーナ
リングフォースを増加させる操作を行う必要がある。(Prior art) In vehicles that tend to understeer, especially when entering a curved road at high speed, the traveling trajectory tends to bulge outward in the direction of the turn, and to prevent this, the driver turns the steering wheel more. Or, if this is not enough, it is necessary to brake the vehicle by depressing the brake pedal to cause a load shift, and to increase the front wheel cornering force by increasing the front wheel load accordingly.
ところで上記の制動操作は車両の進行方向を補正するた
めのブレーキペダル操作であるにもかかわらず、車両を
減速させることにもなり、同時にエンジン回転数の低下
をも惹起して、その後の再加速性能を悪化させる。この
際上手な運転者は、上記のブレーキペダル操作時アクセ
ルペダルをも踏込んでエンジン回転数の低下を防止する
運転技術(俗に言うヒール・アンド・トーであるが、自
動変速機搭載車にあってはブレーキペダルの踏込みを右
足でなく、空いている左足で行うため「左足ブレーキ」
と言う)を使用する。By the way, although the above-mentioned braking operation is a brake pedal operation to correct the direction of travel of the vehicle, it also decelerates the vehicle and at the same time causes a decrease in the engine speed, making it difficult to re-accelerate. worsen performance. In this case, a skilled driver must use the above-mentioned driving technique of pressing down on the accelerator pedal as well to prevent the engine speed from dropping when operating the brake pedal (commonly known as heel-and-toe, but this is not the case with cars equipped with automatic transmissions). This is called "left foot braking" because the brake pedal is pressed with the free left foot instead of the right foot.
).
しかしてこの運転技術はエンジン回転数の低下を防止で
きても、車両の減速は禁じ得す、湾曲路への突入速度や
湾曲路の走破速度の低下が不可避で、高速のまま湾曲路
に突入してこれを走破するという訳にはゆ、かない。However, even if lever driving techniques can prevent a drop in engine speed, it is impossible to decelerate the vehicle, and it is inevitable that the speed at which the vehicle enters a curved road or the speed at which it travels through a curved road will decrease, and it enters a curved road at high speed. There is no way I can run through this.
一方、旋回挙動を制御する技術として従来、特開昭63
−279976号公報により、旋回走行中旋回方向内方
の後輪に制動力を与え、車両の旋回方向におけるヨーレ
ートの発生を補助するようにした装置が提案されている
。この装置は、内側後輪への制動力を高車速で小さく、
低車速で大きくして、高速走行中の旋回安定性と、低速
走行中の小廻り性能とを両立させることを狙ったもので
ある。On the other hand, as a technology for controlling turning behavior, there has been a conventional
Japanese Patent No. 279976 proposes a device that applies braking force to the inner rear wheel in the turning direction during turning to assist in generating a yaw rate in the turning direction of the vehicle. This device reduces the braking force to the inner rear wheel at high vehicle speeds.
The aim is to increase the size at low vehicle speeds to achieve both turning stability at high speeds and maneuverability at low speeds.
(発明が解決しようとする課題)
しかしてこの装置では、旋回走行中の車速か高速ならヨ
ーレートを小さく、低速ならヨーレートを大きくすると
いう、一義的な制御しか期待できず、高速のまま湾曲路
に突入してこれを走破し得るようになす制御は期待でき
ない。(Problem to be solved by the invention) However, with the lever device, only the primary control that can be expected is to reduce the yaw rate if the vehicle speed is high while turning, and increase the yaw rate if the vehicle speed is low. There is no hope for control that will allow the vehicle to enter and run through this area.
本発明はこのような制御を可能にすべく、運転者がヒー
ル・アンド・トー操作を行う間は旋回方向内外輪の制動
力に差をつけて旋回を助長するヨーモーメントを生ぜし
め、これによりブレーキペダル操作が車両の減速を介し
てではなく、直接旋回方向の補正に寄与するようにした
旋回挙動制御装置を提供することを目的とする。In order to enable such control, the present invention creates a yaw moment that promotes turning by differentiating the braking force between the inner and outer wheels in the turning direction while the driver performs a heel-and-toe operation. It is an object of the present invention to provide a turning behavior control device in which a brake pedal operation directly contributes to correction of a turning direction rather than through deceleration of a vehicle.
(課題を解決するための手段)
この目的のため本発明の旋回挙動制御装置は第1図に概
念を示す如く、
アクセル・ペダルの踏込みにより加速し、ブレーキペダ
ルの踏込みにより減速する車両において、アクセルペダ
ルの踏込みを検知するアクセル検知手段と、
ブレーキペダルの踏込みを検知するブレーキ検知手段と
、
車両の旋回状態を検出する旋回状態検出手段と、これら
手段からの信号に応答し、アクセルペダル及びブレーキ
ペダルの双方が踏込まれている間、前記旋回状態に応じ
てこの旋回を助長するヨーモーメントが生ずるよう旋回
方向内外側間で車輪制動力を異らせる内外輪制動力差設
定手段とを具備してなるものである。(Means for Solving the Problems) For this purpose, the turning behavior control device of the present invention, as conceptually shown in FIG. accelerator detection means for detecting depression of the pedal; brake detection means for detecting depression of the brake pedal; turning state detection means for detecting the turning state of the vehicle; and inner and outer wheel braking force difference setting means for differentiating the braking force between the inner and outer wheels in the turning direction so as to generate a yaw moment that promotes the turning depending on the turning state while both of the wheels are being depressed. It is what it is.
(作 用)
アクセルペダル及びブレーキペダルの双方を踏込む高速
旋回希望時、これらの踏込みを夫々検知するアクセル検
知手段及びブレーキ検知手段からの信号に応答して内外
輪制動力差設定手段は、旋回状態検出手段が検出した車
両の旋回状態に応じこの旋回を助長するヨーモーメント
が生ずるよう旋回方向内外側間で車輪制動力を異らせる
。(Function) When a high-speed turn is desired by depressing both the accelerator pedal and the brake pedal, the inner and outer wheel braking force difference setting means responds to signals from the accelerator detection means and the brake detection means, which detect the depression of these pedals, respectively. According to the turning state of the vehicle detected by the state detecting means, the braking force of the wheels is varied between the inner and outer sides in the turning direction so as to generate a yaw moment that promotes the turning.
これにより、アクセルペダル及びブレーキペダルの双方
を踏込む操作によって運転者が希望する通りの旋回軌跡
を車両にトレースさせることができる。そして、ブレー
キペダルの踏込み操作が車両の減速を介してではなく直
接旋回方向の補正に寄与することから、車両の著しい減
速をともなうことなしに上記の目的を達成可能で、高速
のまま湾曲路に突入してこれを走破することができる。This allows the vehicle to trace a turning trajectory desired by the driver by depressing both the accelerator pedal and the brake pedal. In addition, since the depression of the brake pedal directly contributes to correction of the turning direction rather than through deceleration of the vehicle, the above objective can be achieved without significant deceleration of the vehicle, and it is possible to reach the curved road at high speed. You can rush in and run through this.
又上記旋回方向の補正は、ステアリングホイールの修正
操舵量を少なくし、運転者の負担が小さくなると共に、
旋回挙動の乱れを修正する操舵にも余裕が出て、安全上
大いに有益である。In addition, the above-mentioned correction of the turning direction reduces the amount of corrective steering of the steering wheel, reducing the burden on the driver, and
This provides more leeway for steering to correct disturbances in turning behavior, which is greatly beneficial for safety.
(実施例) 以下、本発明の実施例を図面に基き詳細に説明する。(Example) Embodiments of the present invention will be described in detail below with reference to the drawings.
第2図は本発明旋回挙動制御装置の一実施例で、IL、
IRは左右前輪、2L、 2Rは左右後輪、3L、
3Rは前輪ホイールシリンダ、4L、 4Rは後輪ホイ
ールシリンダを夫々示す。又5はブレーキペダル、6は
ブレーキペダルの踏込みで前2輪用の系統7及び後2輪
用の系統8に同時に同じ液圧を出力するマスターシリン
ダで、系7のマスターシリンダ液圧は分岐した系7L、
7Rを経てホイールシリンダ3L。FIG. 2 shows an embodiment of the turning behavior control device of the present invention.
IR is left and right front wheels, 2L, 2R is left and right rear wheels, 3L,
3R indicates the front wheel cylinder, and 4L and 4R indicate the rear wheel cylinders, respectively. Also, 5 is a brake pedal, and 6 is a master cylinder that simultaneously outputs the same hydraulic pressure to system 7 for the front two wheels and system 8 for the two rear wheels when the brake pedal is depressed, and the master cylinder hydraulic pressure for system 7 is branched. Series 7L,
Wheel cylinder 3L via 7R.
3Rに至り前輪IL、 IRを制動し、系8のマスター
シリンダ液圧は分岐した系8L、 8Rを経てホイール
シリンダ4L、 4Rに至り後輪2L、 2Rを制動す
る。3R and brakes the front wheels IL and IR, and the master cylinder hydraulic pressure of system 8 passes through branched systems 8L and 8R to wheel cylinders 4L and 4R, where it brakes the rear wheels 2L and 2R.
かかる通常の前後スプリット弐2系統液圧ブレーキ装置
に対し、本例では系7L、 7R18L、 8Rに夫々
、常態でこれら系を開通してマスターシリンダ液圧をホ
イールシリンダに向かわせる図示の増圧位置を保つ電磁
弁ILL、 IIR,12L、 12Rを挿入する。In contrast to such a normal front and rear split two-system hydraulic brake system, in this example, systems 7L, 7R18L, and 8R are respectively opened to the pressure increasing position shown in the figure, where these systems are normally opened and the master cylinder hydraulic pressure is directed to the wheel cylinder. Insert solenoid valves ILL, IIR, 12L, and 12R that maintain the
これら弁は全て同様な3位置電磁弁とし、対応するソレ
ノイドへの電流(電磁弁駆動電流)i、〜i4が0の時
上記の増圧位置となり、電流i、〜i4が油の時全ての
ボートを遮断してホイールシリンダ内の液圧を不変に保
つ保圧位置となり、電流+ 1 ”” + 4が4Aの
時ホイールシリンダを対応するリザーバタンク13.1
4に通じてホイールシリンダ内の液圧を低下させる減圧
位置になるものとする。These valves are all similar 3-position solenoid valves, and when the current to the corresponding solenoid (electromagnetic valve drive current) i, ~i4 is 0, the above pressure increase position is achieved, and when the current i, ~i4 is oil, all The boat is cut off and the hydraulic pressure in the wheel cylinder is maintained at a pressure holding position, and when the current + 1 "" + 4 is 4A, the wheel cylinder is connected to the corresponding reservoir tank 13.1.
4, the vehicle is assumed to be in a depressurizing position where the hydraulic pressure in the wheel cylinder is reduced.
リザータンク14.15は夫々、共通なモータ15によ
り適宜駆動されるポンプ16.17の吸入ポートに接続
し、上記の減圧中リザーバンク13.14に一時蓄えら
れるブレーキ液をアキュムレータ19.20に戻して系
7,8での再利用に供する。The reservoir tanks 14, 15 are connected to the suction ports of pumps 16, 17 which are appropriately driven by a common motor 15, and the brake fluid temporarily stored in the reservoir banks 13, 14 during the above depressurization is returned to the accumulator 19, 20, and the system is Provided for reuse in 7 and 8.
電磁弁駆動電流i、〜i4はコントローラ21により個
々に決定し、このコントローラには車輪IL、 IR。The electromagnetic valve drive currents i, to i4 are individually determined by a controller 21, which includes wheels IL and IR.
2L、 2Rの回転数ω1〜ω4を夫々検出する車輪速
センサ22〜25からの信号、アクセルペダル(図示せ
ず)の踏込みを検知するアクセルスイッチ26がらの信
号A、ブレーキペダル5の踏込みを検知するブレーキス
イッチ27からの信号B、及びステアリングホイール3
0(第4図に単体で示す)の操舵角θを検出する操舵角
センサ28がらの信号を夫々入力する。Signals from wheel speed sensors 22 to 25 that detect rotational speeds ω1 to ω4 of 2L and 2R, respectively, signal A from the accelerator switch 26 that detects depression of the accelerator pedal (not shown), and detection of depression of the brake pedal 5. signal B from the brake switch 27 and the steering wheel 3.
The signals from the steering angle sensor 28 which detects the steering angle θ of 0 (shown singly in FIG. 4) are respectively input.
コントローラ21はこれら入力情報を基に第3図の制御
プログラムを実行して本発明が目的とする旋回挙動制御
を実現する。The controller 21 executes the control program shown in FIG. 3 based on this input information to realize the turning behavior control aimed at by the present invention.
先ずステップ31〜33では、各車輪IL、 IR,2
L。First, in steps 31 to 33, each wheel IL, IR, 2
L.
2Rの回転数ω1〜ω4、操舵角θ、アクセル信号A及
びブレーキ信号Bを夫々 読込む。次のステップ34で
は、車輪回転数ω1〜ω4から車速■を演算する。この
演算に当っては、ブレーキペダル5を踏込まない非制動
中は非駆動輪である前輪の回転数ω、ω2が車速Vにほ
ぼ対応することから、前輪半径をR,とじた時
V=R,(ω、+ω2)/2
の演算により車速Vを求める。しかして制動中は、前輪
の回転数が必ずしも車速に対応しないことから、アンチ
スキッド制御で通常行われている手法により疑似車速を
求め、これを車速Vとして用いる。2R's rotational speed ω1 to ω4, steering angle θ, accelerator signal A, and brake signal B are read respectively. In the next step 34, the vehicle speed ■ is calculated from the wheel rotational speeds ω1 to ω4. In this calculation, since the rotational speed ω, ω2 of the front wheel, which is a non-driving wheel, approximately corresponds to the vehicle speed V during non-braking when the brake pedal 5 is not depressed, when the front wheel radius is R, V= The vehicle speed V is determined by calculating R, (ω, +ω2)/2. During braking, however, the number of revolutions of the front wheels does not necessarily correspond to the vehicle speed, so a pseudo vehicle speed is determined using a method commonly used in anti-skid control, and this is used as the vehicle speed V.
ステップ35では、アクセル信号A及びブレーキ信号B
が共に1か否かにより、運転者がアクセルペダル及びブ
レーキペダルの双方を踏込んだヒール・アンド・トー(
左足ブレーキ)操作を行っているか否かチエツクする。In step 35, the accelerator signal A and the brake signal B
Heel-and-toe (when the driver depresses both the accelerator pedal and the brake pedal) depends on whether both are 1 or not.
Check whether the left foot brake is being operated.
この操作を行っていなければ、本発明による旋回挙動制
御が不要であることから、ステップ36で電磁弁駆動電
流11〜i4を全て0とし、これをステップ40で出力
する。この場合、電磁弁11L、 IIR,12L、
12Rは夫々図示の増圧位置となって、各車輪のホイー
ルシリンダ液圧をマスターシリンダ6よりの液圧に依存
させることから、通常の制動が可能である。If this operation is not performed, the turning behavior control according to the present invention is not necessary, so the solenoid valve drive currents 11 to i4 are all set to 0 in step 36 and outputted in step 40. In this case, solenoid valves 11L, IIR, 12L,
12R is at the pressure increasing position shown in the figure, and the wheel cylinder hydraulic pressure of each wheel is made to depend on the hydraulic pressure from the master cylinder 6, so that normal braking is possible.
ステップ35でヒール・アンド・トー(左足ブレーキ)
操作中であると判別した場合、以下の如くに本発明が狙
いとする旋回挙動制御を行う。即ち、ステップ37で旋
回方向内側車輪の電磁弁駆動電流+1+IJ(左旋回時
)又は12+ 14 (右旋回時)を0にして内側車輪
の制動力(ホイールシリンダ液圧)を第7図に示す如く
ブレーキペダル踏込力にまかせる。Heel and toe (left foot brake) at step 35
If it is determined that the vehicle is in operation, the turning behavior control aimed at by the present invention is performed as follows. That is, in step 37, the solenoid valve drive current +1+IJ (when turning left) or 12+14 (when turning right) of the inner wheel in the turning direction is set to 0, and the braking force (wheel cylinder hydraulic pressure) of the inner wheel is shown in FIG. Just leave it to the force of pressing the brake pedal.
しかして、旋回方向外側車輪の制動力はこれを減じて、
内側車輪との制動力差により旋回方向のヨーモーメント
を生じさせるために、ステップ38で旋回状態をチエツ
クしてどの領域での旋回状態かを判定する。この判定は
当然操舵角θ及び車速Vを基に行うが、操舵角θについ
てはこれを第4図及び第5図に示す如くステアリングホ
イール30の中立位置からの切り角が±θl (+は左
操舵、−は右操舵、を表す)未満の小舵角域と、±θ1
以上、±θ2未満の中舵角域と、±θ2以上、±θ。Therefore, the braking force of the outer wheel in the turning direction is reduced,
In order to generate a yaw moment in the turning direction due to the difference in braking force with the inner wheel, the turning state is checked in step 38 to determine in which region the turning state is occurring. This determination is naturally made based on the steering angle θ and the vehicle speed V, but as shown in FIGS. 4 and 5, the turning angle from the neutral position of the steering wheel 30 is ±θl (+ indicates left (- means right steering) and a small steering angle range less than ±θ1
Above, medium steering angle range less than ±θ2, and ±θ2 or more, ±θ.
(θ、は操舵限界)以下の大舵角域とに3分割し、車速
■についてもこれを第5図に示す如<V+未満の低車速
域と、V、以上、■2未満の中車速域と、12以上の高
車速域とに3分割する。上記の判定は、これら舵角域と
車速域との組合せにより定めた第5図に示す如きa、b
、c、d令Jf域のうちどの領域での旋回状態であるか
を判定する。(θ is the steering limit) The vehicle speed is divided into 3 large steering angle ranges as shown in Figure 5. The vehicle speed range is divided into 3 regions: 12 and 12 or higher vehicle speed regions. The above judgment is based on the combinations of these steering angle ranges and vehicle speed ranges, a and b as shown in Figure 5.
, c, and d-order Jf ranges, it is determined in which region the turning state is occurring.
次のステップ39では、このようにして判定した領域(
旋回状態)に応じ、ヒール・アンド・ト−(左足ブレー
キ)操作で運転者が必要とするヨーモーメント(旋回方
向への挙動補正)を得るための旋回方向外側車輪の制動
力制限程度、つまり当該車輪用電磁弁駆動電流j2+
14 (左旋回時)又はjl+ 13 (右旋回時)の
パターンを第6図のテーブルデータからルックアップす
る。このテーブルデータは、ステップ38で判定した領
域(旋回状態)毎に外側車輪用電磁弁駆動電流iz+
L又は11+ 13を何m5ec間0^にして外側車輪
の電磁弁11L、 12L又はIIR,12Rを増圧位
置にし、何m5ec間2Aにして同電磁弁を保圧位置に
するサイクルを繰返すかのパターンを定めたもので、保
圧位置の時間割合が高い程、外側車輪の制動力が大きく
制限されて大きな旋回方向ヨーモーメントを生ずる。そ
して、このヨーモーメントがヒール・アンド・トー(左
足ブレーキ)操作によって要求される旋回挙動補正量に
対応するよう上記保圧位置の時間割合を決定する。第5
図に示す如く、車速をV。、操舵角をθ。にしたX点で
の旋回状態を例にとって説明すると、この旋回状態はc
領域に相当し、従って第6図から明らかなように外側車
輪用電磁弁駆動電流は3 m5ecの間OAにし、10
m5ecの間加にするサイクルを繰返す第7図の如きパ
ターンに決定されることとなる。In the next step 39, the area determined in this way (
The degree of braking force restriction on the outer wheels in the turning direction in order to obtain the yaw moment (behavior correction in the turning direction) required by the driver by heel-and-toe (left foot braking) operation, depending on the turning condition), that is, the relevant Wheel solenoid valve drive current j2+
14 (when turning left) or jl+13 (when turning right) is looked up from the table data in FIG. This table data shows the outer wheel solenoid valve drive current iz+ for each region (turning state) determined in step 38.
For how many m5ec should L or 11+13 be kept at 0^, solenoid valves 11L, 12L or IIR, 12R on the outer wheels should be set to the pressure increasing position, and for how many m5ec should the cycle be kept at 2A and the same solenoid valve should be set to the pressure holding position? The pattern is determined, and the higher the time ratio of the pressure holding position, the more the braking force of the outer wheels is restricted and the larger the yaw moment in the turning direction is generated. Then, the time ratio of the pressure holding position is determined so that this yaw moment corresponds to the turning behavior correction amount required by the heel-and-toe (left foot brake) operation. Fifth
As shown in the figure, the vehicle speed is V. , the steering angle is θ. To explain the turning state at point X as an example, this turning state is c
Therefore, as is clear from Fig. 6, the outer wheel solenoid valve driving current is OA for 3 m5ec, and
The pattern shown in FIG. 7, which repeats the cycle of adding m5ec, is decided upon.
ステップ37.39で決定した電磁弁駆動電流i、〜i
4はステップ40で対応する電磁弁11L、 IIR,
12L。Solenoid valve drive current i, ~i determined in step 37.39
4 is the corresponding solenoid valve 11L, IIR,
12L.
12Rへ出力され、対応車輪を個々に制動する。ところ
で、上述した処から明らかなように旋回方向内側車輪の
制動力(ホイールシリンダ液圧)は第7図の如くブレー
キペダル5の踏力に対応した値となるが、旋回方向外側
車輪の制動力(ホイールシリンダ液圧)は同図に例示さ
れる如くブレーキペダル5の踏力に対応した値より小さ
くされることから、車両は旋回方向のヨーモーメントを
受けて旋回を助長され、ヒール・アンド・トー操作によ
り狙った通りの旋回走行を行うことができる。It is output to 12R and brakes the corresponding wheels individually. By the way, as is clear from the above, the braking force (wheel cylinder hydraulic pressure) on the inner wheel in the turning direction has a value corresponding to the depression force of the brake pedal 5 as shown in FIG. As illustrated in the figure, since the wheel cylinder hydraulic pressure is made smaller than the value corresponding to the depression force of the brake pedal 5, the vehicle receives a yaw moment in the turning direction and is encouraged to turn, resulting in heel-and-toe operation. This allows you to make the desired turn.
しかして、ヒール・アンド・トー操作によるブレーキペ
ダルの踏込みが車両の減速を介してではなく、直接ヨー
モーメントの発生、つまり旋回方向の補正に寄与するこ
とから、減速をほとんどともなうことな(、高速のまま
湾曲路に突入してこれを走破することができる。However, pressing the brake pedal during heel-and-toe operation does not decelerate the vehicle, but directly generates a yaw moment, that is, contributes to correcting the turning direction. You can enter a curved road and drive through it.
なお、上述の例では左又は右の前後輪を共通に制動力制
限することとしたが、前輪のみ又は後輪のみを内外輪間
で制動力に差が生ずるよう制御しても良いことは言うま
でもない、又、ヒール・アンド・トー(左足ブレーキ)
操作中、ステアリングホイールを切戻して逆方向の旋回
に入った場合は、高くされていたホイールシリンダ液圧
を急低下させる必要を生ずるが、この目的のためには対
応する側の電磁弁を一時減圧位置にして目的を達成する
ことができる。更に、高くすべきホイールシリンダ液圧
は別途設けた増圧手段によりマスク−シリンダ液圧より
高くして、−層大きなヨーモーメントを発生させるよう
にすることもできる。Note that in the above example, the braking force is commonly limited for the left or right front and rear wheels, but it goes without saying that it is also possible to control only the front wheels or only the rear wheels so that there is a difference in braking force between the inner and outer wheels. Also, heel and toe (left foot brake)
During operation, if the steering wheel is turned back and a turn is made in the opposite direction, it will be necessary to suddenly reduce the wheel cylinder fluid pressure, which had been set high, but for this purpose, the solenoid valve on the corresponding side must be temporarily turned off. You can achieve your goal by placing it in the reduced pressure position. Furthermore, the wheel cylinder hydraulic pressure to be increased can be made higher than the mask cylinder hydraulic pressure by means of a separately provided pressure increasing means, thereby generating an even greater yaw moment.
加えて、車両の旋回状態を判定するに当り、第5図の如
く操舵量と車速との組合せを用いる代りに、操舵量と車
体横加速度との組合せを用いて領域判定を行うこともで
きること勿論である。In addition, in determining the turning state of the vehicle, it is of course possible to perform region determination using a combination of the steering amount and vehicle lateral acceleration instead of using the combination of the steering amount and vehicle speed as shown in FIG. It is.
第8図は本発明の他の例を示し、本例は2系統液圧ブレ
ーキ装置の前輪ホイールシリンダ配管7L。FIG. 8 shows another example of the present invention, and this example shows front wheel cylinder piping 7L of a two-system hydraulic brake system.
7Rのみに常開の電磁開閉弁41L、 411’lを挿
入し、この弁をコントローラ42で開閉制御して前記実
施例と同様の作用効果が得られるような簡単な構成とす
る。そして、コントローラ42にはアクセルスイッチ2
6からの信号A、ブレーキスイッチ27からの信号B、
操舵角センサ28からの信号、及び車速■を検出する車
速センサ43からの信号を夫り入力する。A normally open electromagnetic on-off valve 41L, 411'l is inserted only in 7R, and the opening/closing of this valve is controlled by the controller 42, so that a simple structure can be obtained to obtain the same effect as in the previous embodiment. The controller 42 includes an accelerator switch 2.
Signal A from 6, signal B from brake switch 27,
A signal from the steering angle sensor 28 and a signal from a vehicle speed sensor 43 that detects the vehicle speed (2) are input.
コントロ・−ラ42は、A=1且つB=1となるヒール
・アンド・トー(左足ブレーキ)操作中、操舵角θが設
定値以上で、車速■も設定値以上である旋回状態であれ
ば、旋回方向外側前輪IL (右旋回申)又はIR(左
旋回中)の開閉弁41L又は41Rを閉じて旋回方向の
ヨーモーメントを生じさせるプログラムにより、前記実
施例と同様の作用効果が得られるようにする。但し、本
例では制御が大まかで、きめ細かな旋回挙動の制御を得
難いが、構成の大幅な簡易化及び低廉化を図ることがで
きる。During a heel-and-toe (left foot brake) operation where A=1 and B=1, the controller 42 is in a turning state where the steering angle θ is greater than the set value and the vehicle speed ■ is also greater than the set value. The same effect as in the above embodiment can be obtained by a program that closes the on-off valve 41L or 41R of the outer front wheel in the turning direction IL (turning right) or IR (turning left) to generate a yaw moment in the turning direction. do it like this. However, in this example, the control is rough and it is difficult to obtain fine control of turning behavior, but the configuration can be significantly simplified and lowered in cost.
(発明の効果)
かくして本発明旋回挙動制御装置は上述の如く、ヒール
・アンド・トー(左足ブレーキ)操作を行うような旋回
中、旋回を助長するようなヨーモーメントが生ずるよう
旋回方向内外側で車輪制動力を異らせる構成にしたから
、ブレーキ操作が車両の減速を介してではなく、直接旋
回方向の補正に寄与することとなり、車速の著しい低下
をともなうことなく、旋回方向の補正が実現でき、高速
のまま湾曲路に突入してこれを走破することが可能とな
る。(Effects of the Invention) Thus, as described above, the turning behavior control device of the present invention, during a turn such as performing a heel-and-toe (left foot brake) operation, controls the turning behavior in the inner and outer directions in the turning direction so as to generate a yaw moment that promotes the turning. Since the wheel braking force is configured to vary, the brake operation directly contributes to correcting the turning direction rather than through vehicle deceleration, making it possible to correct the turning direction without significantly reducing vehicle speed. This makes it possible to enter and traverse curved roads at high speed.
又、かかる旋回方向の補正は、ステアリングホイールの
修正操舵量を少なくし得て、運転者の負担軽減に寄与す
ると共に、旋回挙動の乱れを修正する操舵にも余裕が出
て安全上大いに有益である。In addition, such correction of the turning direction can reduce the amount of corrective steering of the steering wheel, which contributes to reducing the burden on the driver, and also provides leeway for steering to correct disturbances in turning behavior, which is greatly beneficial for safety. be.
第1図は本発明旋回挙動制御装置の概念図、第2図は本
発明装置の一実施例を示すシステム図、
第3図は同側におけるコントロールの制御プログラムを
示すフローチャート、
第4図は操舵角区分図、
第5図は旋回状態の領域線図、
第6図は領域毎の外側車輪用電磁弁駆動電流のパターン
図、
第7図は第2図のシステムによる旋回挙動制御の動作タ
イムチャート、
第8図は本発明の他の例を示す第2図と同様なシステム
図である。
IL、 IR・・・前輪 2L、 2R・・・
後輪3L、 3R,4L、 4R・・・ホイールシリン
ダ5・・・ブレーキペダル 6・・・マスターシリン
ダILL、 IIR,12L、 12R・・・電磁弁1
3、14・・・リザーバタンク
15・・・モータ 16.17・・・ポンプ
19、20・・・アキュムレータ
21・・・コントローラ 22〜25・・・車輪速
センサ26・・・アクセルスインチ 27・・・ブレー
キスイッチ28・・・操舵角センサ
30・・・ステアリングホイール
41L、 41R・・・電磁開閉弁 42・・・コント
ローラ43・・・車速センサ
@I
図
第3図
第4
図
第5図
@6
図
第7図Fig. 1 is a conceptual diagram of the turning behavior control device of the present invention, Fig. 2 is a system diagram showing an embodiment of the device of the present invention, Fig. 3 is a flowchart showing a control program for control on the same side, and Fig. 4 is a steering Corner division diagram, Figure 5 is a region diagram of the turning state, Figure 6 is a pattern diagram of the outer wheel solenoid valve drive current for each region, and Figure 7 is an operation time chart of turning behavior control by the system in Figure 2. , FIG. 8 is a system diagram similar to FIG. 2 showing another example of the present invention. IL, IR...Front wheel 2L, 2R...
Rear wheels 3L, 3R, 4L, 4R...Wheel cylinder 5...Brake pedal 6...Master cylinder ILL, IIR, 12L, 12R...Solenoid valve 1
3, 14...Reservoir tank 15...Motor 16.17...Pump 19, 20...Accumulator 21...Controller 22-25...Wheel speed sensor 26...Accelerator inch 27. ...Brake switch 28...Steering angle sensor 30...Steering wheel 41L, 41R...Solenoid on-off valve 42...Controller 43...Vehicle speed sensor @I Figure 3 Figure 4 Figure 5 @ 6 Figure 7
Claims (1)
ダルの踏込みにより減速する車両において、 アクセルペダルの踏込みを検知するアクセル検知手段と
、 ブレーキペダルの踏込みを検知するブレーキ検知手段と
、 車両の旋回状態を検出する旋回状態検出手段と、これら
手段からの信号に応答し、アクセルペダル及びブレーキ
ペダルの双方が踏込まれている間、前記旋回状態に応じ
てこの旋回を助長するヨーモーメントが生ずるよう旋回
方向内外側間で車輪制動力を異らせる内外輪制動力差設
定手段とを具備してなることを特徴とする車両の旋回挙
動制御装置。1. In a vehicle that accelerates when the accelerator pedal is depressed and decelerates when the brake pedal is depressed, the present invention includes an accelerator detection means that detects the depression of the accelerator pedal, a brake detection means that detects the depression of the brake pedal, and a turning state that detects the turning state of the vehicle. and a state detection means, and in response to the signals from these means, while both the accelerator pedal and the brake pedal are depressed, a yaw moment that promotes the turning is generated according to the turning state between the inside and outside in the turning direction. A turning behavior control device for a vehicle, comprising means for setting a difference in braking force between inner and outer wheels for differentiating wheel braking force.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1250646A JP2572857B2 (en) | 1989-09-28 | 1989-09-28 | Vehicle turning behavior control device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1250646A JP2572857B2 (en) | 1989-09-28 | 1989-09-28 | Vehicle turning behavior control device |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP8124604A Division JP2723104B2 (en) | 1996-05-20 | 1996-05-20 | Vehicle turning behavior control device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH03112757A true JPH03112757A (en) | 1991-05-14 |
JP2572857B2 JP2572857B2 (en) | 1997-01-16 |
Family
ID=17210955
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1250646A Expired - Lifetime JP2572857B2 (en) | 1989-09-28 | 1989-09-28 | Vehicle turning behavior control device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2572857B2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04372447A (en) * | 1991-06-19 | 1992-12-25 | Mitsubishi Motors Corp | Brake device for automobile |
JP2011073605A (en) * | 2009-09-30 | 2011-04-14 | Advics Co Ltd | Motion control device of vehicle |
JP2016150711A (en) * | 2015-02-19 | 2016-08-22 | 富士重工業株式会社 | Brake override system |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63279976A (en) * | 1987-05-12 | 1988-11-17 | Toyota Motor Corp | Steering device for vehicle |
JPS6460475A (en) * | 1987-08-31 | 1989-03-07 | Toyota Motor Corp | Auxiliary equipment for driving vehicle |
JPS6485862A (en) * | 1987-07-03 | 1989-03-30 | Mazda Motor | Slip control device for automobile |
-
1989
- 1989-09-28 JP JP1250646A patent/JP2572857B2/en not_active Expired - Lifetime
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63279976A (en) * | 1987-05-12 | 1988-11-17 | Toyota Motor Corp | Steering device for vehicle |
JPS6485862A (en) * | 1987-07-03 | 1989-03-30 | Mazda Motor | Slip control device for automobile |
JPS6460475A (en) * | 1987-08-31 | 1989-03-07 | Toyota Motor Corp | Auxiliary equipment for driving vehicle |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04372447A (en) * | 1991-06-19 | 1992-12-25 | Mitsubishi Motors Corp | Brake device for automobile |
JP2011073605A (en) * | 2009-09-30 | 2011-04-14 | Advics Co Ltd | Motion control device of vehicle |
JP2016150711A (en) * | 2015-02-19 | 2016-08-22 | 富士重工業株式会社 | Brake override system |
Also Published As
Publication number | Publication date |
---|---|
JP2572857B2 (en) | 1997-01-16 |
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