WO1997002970A1 - Hydraulic braking system with electrically switched hydraulic valves - Google Patents

Hydraulic braking system with electrically switched hydraulic valves Download PDF

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Publication number
WO1997002970A1
WO1997002970A1 PCT/EP1996/002687 EP9602687W WO9702970A1 WO 1997002970 A1 WO1997002970 A1 WO 1997002970A1 EP 9602687 W EP9602687 W EP 9602687W WO 9702970 A1 WO9702970 A1 WO 9702970A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
hydraulic
switching
valves
hydraulic valves
Prior art date
Application number
PCT/EP1996/002687
Other languages
German (de)
French (fr)
Inventor
Georg Sonnenschein
Original Assignee
Itt Automotive Europe Gmbh
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Itt Automotive Europe Gmbh filed Critical Itt Automotive Europe Gmbh
Publication of WO1997002970A1 publication Critical patent/WO1997002970A1/en

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Classifications

    • 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
    • B60T8/32—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 a speed condition, e.g. acceleration or deceleration
    • B60T8/34—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • 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
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/10—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with fluid assistance, drive, or release
    • B60T13/66—Electrical control in fluid-pressure brake systems
    • B60T13/68—Electrical control in fluid-pressure brake systems by electrically-controlled valves
    • B60T13/686—Electrical control in fluid-pressure brake systems by electrically-controlled valves in hydraulic systems or parts thereof
    • 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
    • B60T8/32—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 a speed condition, e.g. acceleration or deceleration
    • B60T8/34—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/363—Electromagnetic valves specially adapted for anti-lock brake and traction control systems in hydraulic systems
    • 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
    • B60T8/32—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 a speed condition, e.g. acceleration or deceleration
    • B60T8/34—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/42—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having expanding chambers for controlling pressure, i.e. closed systems
    • B60T8/4275—Pump-back systems
    • 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
    • B60T8/32—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 a speed condition, e.g. acceleration or deceleration
    • B60T8/34—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5006—Pressure reapplication by pulsing of valves
    • 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
    • B60T8/32—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 a speed condition, e.g. acceleration or deceleration
    • B60T8/34—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/50—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 a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition having means for controlling the rate at which pressure is reapplied to or released from the brake
    • B60T8/5075—Pressure release by pulsing of valves

Definitions

  • Hydraulic brake system with electrically switchable hydraulic valves
  • the invention relates to a hydraulic brake system with electrically switchable hydraulic valves, which are provided for modulating the brake pressure in the wheel brakes for the purpose of anti-lock control, traction control or the like.
  • Such brake systems are known in a variety of designs.
  • brake pressure modulation e.g. Electrically actuable 2/2-way valves, i.e. Hydraulic valves that only know two switching positions (open or closed) are used. If anti-lock control or traction control is carried out with such valves, the pressure build-up and pressure reduction gradients can be influenced in the desired manner by controlling the hydraulic valves with low-frequency pulse sequences and varying the pulse duration / pause ratio.
  • a pair of valves namely an inlet and an outlet valve, is provided for each controllable wheel, the inlet valve, which is inserted in the brake line between the master cylinder and the wheel brake, advantageously being switched to passage in its rest position and when one is applied Voltage changes to the blocking state.
  • the outlet valve which is used to reduce pressure, is blocked in the rest position.
  • a disadvantage of the brake pressure control with the aid of such fast-switching hydraulic valves is that the fast armature movements during the transition from one end position to the other, local deceleration and acceleration of the hydraulic fluid, transmission of the pulsation to components (structure-borne noise) etc. result in noise ⁇ stand, which are perceived as a nuisance with anti-lock or traction control.
  • the noise level is largely determined by the changeover speed from one end position to the other.
  • the present invention has for its object to reduce or significantly reduce the annoying noises caused by the rapid switching of the valve lifters of these hydraulic valves from one end position to the other in a simple manner and without an adverse influence on the brake pressure control.
  • the special feature of the brake system according to the invention is that the Switchover of the hydraulic valves or the valve tappet from one end position to the other is effected by an alternating signal which is only present for the duration of the switchover and which delays the switchover process in comparison to a pure “switching on or off” of the valve; after the switchover or after a predetermined switchover time period, a permanent signal ('1' or '0') is then present again at the hydraulic valve.
  • a pulse sequence is provided as the alternating signal, the frequency of which is high or the pulse times and pulse pauses are short in comparison to the time period required for the switching process.
  • FIGS. 1 and 2 shows in detail an embodiment of an inlet valve of the brake system according to FIGS. 1 and
  • Fig. 3 diagrams to illustrate the control of the intake or exhaust valve of the brake system according to the invention.
  • a wheel brake 1 only those components of a block reproduced ski-protected brake system, which are necessary for the explanation of the invention.
  • the connection of a wheel brake 1 to a brake circuit I of a master cylinder 2 of a hydraulic brake system is shown.
  • the master cylinder 2 is actuated by an upstream vacuum booster 3 with the aid of a brake pedal 4.
  • the pressure in the wheel brake 1 is controlled by means of an intake valve 5 and an exhaust valve 6. In their rest position, the inlet valve 5 is switched to passage, the outlet valve 6 to block.
  • FIG. 2 A longitudinal section through the valve is shown here. It essentially consists of a valve armature 9, which is mounted axially displaceably in a valve housing 10. A valve tappet 11 is part of this armature 9. The armature 9 with the valve tappet 11 is held in its rest position by the force of a coil spring 12, in which there is a hydraulic connection from a hydraulic connection or input 13 to an outlet 14. The connection 13 leads to the main cylinder 2, the outlet 14 to the wheel brake 1.
  • the hydraulic valve 5 according to FIG. 2 has a valve actuation coil 15 and a magnetic core 16.
  • the valve armature 9 and the magnetic core 16 are separated by an air gap 17, the design of which is essential for the valve characteristics.
  • the electrical valve connections are 15a, 15b draws.
  • valve armature 9 When the valve is actuated by applying a voltage to the valve coil 15, a force is exerted on the valve armature 9, which leads to the axial displacement of the valve tappet into its second end position. The pressure medium passage from the inlet 13 to the outlet 14 is closed.
  • While hydraulic valves of the type described here have hitherto been switched over by applying a voltage or switching off, the corresponding signal being maintained as a permanent signal after switching over to the second end position until switching back, according to the invention at time t ⁇ an alternating signal applied.
  • the changeover signal After a predetermined period of time in which the switchover process is to be ended, or after the actual switchover time ti ⁇ t 2 , the changeover signal then changes into a continuous signal which holds the valve in the switchover position or the valve tappet in the second end position.
  • an alternating signal is again applied in an analog manner and then the continuous signal.
  • the invention is based on the consideration that e.g. in an inlet valve of the type shown in Fig. 2 when the voltage is applied to the coil 15 due to the coil inductance
  • the switching is therefore brought about with the aid of the alternating signal or a pulse sequence.
  • the ram movement is thereby slowed down.
  • the tappet movement starts when the switching voltage is applied. If the tension is reduced in the changeover phase - due to a decreasing tension amplitude or a pulse pause - the ram is braked by the return spring and by the pressure in the hydraulic system. The newly increasing voltage or the following pulse then again increase the force acting on the plunger in the closing direction.
  • the alternating signal results in a gradual, overall delayed closing or opening of the valve and a relatively "gentle" stop in the end positions.
  • the task of reducing valve noise significantly is solved in this way.
  • the 'setpoint' of the valve position is shown. At time ti it is clear that the valve should switch over, at time t 4 the downshift begins.
  • Diagram 'B' in FIG. 3 shows the course of the voltage applied to the coil as specified in accordance with the invention.
  • an alternating signal here a pulsed alternating signal, which occurs at time t 2 when the closing process has ended , changes to a continuous signal.
  • the downshift takes place in an analogous manner; pulses are again present in the time period t 4 to t 5 .
  • FIG. 3 The diagrams' C and 'D' in Fig. 3 show the course of the current through the coil 15 (FIG. 2) and the course of the magnetic field strength caused by the voltage course according to 'B'.
  • the change in current due to the alternating signal is only first ended at time t 3 or t 6 .
  • valve path or ram path is plotted in diagram 'E' in FIG. 3. It can be seen that the influence of the alternating signal results in a substantial slowdown of the valve tappet movement; the time spans tj to t 2 and t 4 to t 5 are necessary in order to transfer the valve tappet from one end position to the other end position.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Magnetically Actuated Valves (AREA)

Abstract

The invention concerns a hydraulic braking system with electrically switched hydraulic valves (5, 6) which are used to modulate the braking pressure in the wheel brakes. A change-over signal which delays the switching process (t1 - t2; t4 - t5) in comparison with conventional switching is applied in order to switch over these hydraulic valves (5, 6) from one end setting to the other. After this delayed switching of the valve or after a predetermined switching duration, a continuous signal ('1' or '0') is applied.

Description

Hydraulische Bremsanlage mit elektrisch umschaltbaren Hy¬ draulikventilenHydraulic brake system with electrically switchable hydraulic valves
Die Erfindung bezieht sich auf eine hydraulische Bremsanlage mit elektrisch umschaltbaren Hydraulikventilen, die zur Mo¬ dulation des Bremsdruckes in den Radbremsen zwecks Blockier- schutzregelung, Antriebsschlupfregelung oder dergl. vorgese¬ hen sind.The invention relates to a hydraulic brake system with electrically switchable hydraulic valves, which are provided for modulating the brake pressure in the wheel brakes for the purpose of anti-lock control, traction control or the like.
Derartige Bremsanlagen sind in vielfältiger Ausgestaltung bekannt. Zur Bremsdruckmodulation werden z.B. elektromagne¬ tisch betätigbare 2/2-Wegeventile, d.h. Hydraulikventile, die nur zwei Schaltpositionen (offen oder geschlossen) ken¬ nen, verwendet. Wird mit solchen Ventilen eine Blockierschutz- oder eine Antriebsschlupfregelung durchge¬ führt, läßt sich der Druckaufbau- und der Druckabbaugradient durch Ansteuerung der Hydraulikventile mit niederfrequenten Pulsfolgen und Variieren der Pulsdauer-/Pulspausenverhält- nisse in der gewünschten Weise beeinflussen.Such brake systems are known in a variety of designs. For brake pressure modulation e.g. Electrically actuable 2/2-way valves, i.e. Hydraulic valves that only know two switching positions (open or closed) are used. If anti-lock control or traction control is carried out with such valves, the pressure build-up and pressure reduction gradients can be influenced in the desired manner by controlling the hydraulic valves with low-frequency pulse sequences and varying the pulse duration / pause ratio.
Im allgemeinen ist für jedes regelbare Rad ein Ventilpaar, nämlich ein Einlaß- und ein Auslaßventil vorgesehen, wobei das Einlaßventil, das in der Bremsleitung zwischen dem Hauptzylinder und der Radbremse eingefügt ist, zweckmäßiger¬ weise in seiner Ruhestellung auf Durchlaß geschaltet ist und beim Anlegen einer Spannung in den Sperrzustand übergeht. Das Auslaßventil, das zum Druckabbau dient, ist dagegen in der Ruhestellung gesperrt. Ein Nachteil der Bremsdruckregelung mit Hilfe solcher schnellschaltenden Hydraulikventile besteht darin, daß durch die schnellen Ankerbewegungen beim Übergang von der einen in die andere Endposition, durch örtliche Verzögerung und Be¬ schleunigung der hydraulischen Flüssigkeit, Übertragung der Pulsation auf Bauteile (Körperschall) usw. Geräusche ent¬ stehen, die bei einer Blockierschutz- oder Antriebsschlupf- regelung als störend empfunden werden. Die Geräuschstärke wird maßgeblich von der Umschaltgeschwindigkeit von der ei¬ nen in die andere Endposition bestimmt.In general, a pair of valves, namely an inlet and an outlet valve, is provided for each controllable wheel, the inlet valve, which is inserted in the brake line between the master cylinder and the wheel brake, advantageously being switched to passage in its rest position and when one is applied Voltage changes to the blocking state. The outlet valve, which is used to reduce pressure, is blocked in the rest position. A disadvantage of the brake pressure control with the aid of such fast-switching hydraulic valves is that the fast armature movements during the transition from one end position to the other, local deceleration and acceleration of the hydraulic fluid, transmission of the pulsation to components (structure-borne noise) etc. result in noise ¬ stand, which are perceived as a nuisance with anti-lock or traction control. The noise level is largely determined by the changeover speed from one end position to the other.
Aus der DE 42 36 047 AI (P 7397) ist bereits eine Bremsanla¬ ge mit Blockierschutz- und/oder Antriebsschlupfregelung be¬ kannt, deren Hydraulikventile, wenn sie aus der Ruhelage heraus auf Sperren oder Durchlaß umgeschaltet werden sol¬ len, mit einem Wechselsignal oder einer Pulsfolge angesteu¬ ert werden, dessen Frequenz bzw. deren Pulsdauer-/Pulspau- senverhältnis auf die Charakteristik der Ventile abgestimmt ist. Der Ventilstößel nimmt unter dem Einfluß des Wechsel¬ signals oder der Pulsfolge eine Dosierstellung ein, die wie¬ derum durch Variieren der Frequenz bzw. des Pulsdauer-/Puls- pausenverhältnisses beeinflußt werden kann. Auf diese Weise werden die Ventilgeräusche erheblich reduziert.From DE 42 36 047 AI (P 7397) a brake system with anti-lock and / or traction control system is already known, the hydraulic valves of which, when they are to be switched from the idle position to blocking or passage, with an alternating signal or a pulse sequence can be controlled, the frequency or the pulse duration / pulse interval ratio of which is matched to the characteristics of the valves. Under the influence of the alternating signal or the pulse sequence, the valve lifter assumes a metering position, which in turn can be influenced by varying the frequency or the pulse duration / pulse pause ratio. This significantly reduces valve noise.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, die störenden Geräusche, die durch das schnelle Umschalten der Ventilstößel dieser Hydraulikventile von der einen in die andere Endposition hervorgerufen werden, auf einfache Weise und ohne nachteiligen Einfluß auf die Bremsdruckregelung zu mindern oder entscheidend zu verringern.The present invention has for its object to reduce or significantly reduce the annoying noises caused by the rapid switching of the valve lifters of these hydraulic valves from one end position to the other in a simple manner and without an adverse influence on the brake pressure control.
Es hat sich gezeigt, daß diese Aufgabe durch die im Anspruch 1 beschriebenen Maßnahmen zu lösen ist. Das Besondere der erfindungsgemäßen Bremsanlage besteht also darin, daß die Umschaltung der Hydraulikventile bzw. des Ventilstößels von der einen in die andere Endstellung durch ein Wechselsignal bewirkt wird, das nur für die Dauer der Umschaltung anliegt und das den Umschaltvorgang im Vergleich zu einem reinen "Ein- bzw. Ausschalten" des Ventils verzögert; nach dem Um¬ schalten oder nach einer vorgegebenen Umschaltzeitdauer liegt dann an dem Hydraulikventil wieder ein Dauersignal ('1' oder '0') an.It has been shown that this problem can be solved by the measures described in claim 1. The special feature of the brake system according to the invention is that the Switchover of the hydraulic valves or the valve tappet from one end position to the other is effected by an alternating signal which is only present for the duration of the switchover and which delays the switchover process in comparison to a pure “switching on or off” of the valve; after the switchover or after a predetermined switchover time period, a permanent signal ('1' or '0') is then present again at the hydraulic valve.
Nach einem vorteilhaften Ausführungsbeispiel der Erfindung ist als Wechselsignal eine Pulsfolge vorgesehen, deren Fre¬ quenz hoch ist bzw. deren Pulszeiten und Pulspausen kurz sind im Vergleich zu der für den Umschaltvorgang benötigten Zeitdauer.According to an advantageous embodiment of the invention, a pulse sequence is provided as the alternating signal, the frequency of which is high or the pulse times and pulse pauses are short in comparison to the time period required for the switching process.
Weitere Merkmale, Vorteile und Anwendungsmöglichkeiten der Erfindung gehen aus der folgenden Darstellung eines Ausfüh¬ rungsbeispiels anhand der beigefügten Abbildungen hervor.Further features, advantages and possible uses of the invention can be seen from the following illustration of an exemplary embodiment with the aid of the attached figures.
Es zeigenShow it
Fig. 1 schematisch vereinfacht und als Teildarstellung die wichtigsten hydraulischen Komponenten einer Brems¬ anlage nach der Erfindung und deren hydraulische Zusammenschaltung,1 schematically simplified and as a partial representation the most important hydraulic components of a brake system according to the invention and their hydraulic interconnection,
Fig. 2 im Detail ein Ausführungsbeispiel eines Einlaßven¬ tils der Bremsanlage nach Fig. 1 und2 shows in detail an embodiment of an inlet valve of the brake system according to FIGS. 1 and
Fig. 3 Diagramme zur Veranschaulichung der Ansteuerung des Einlaß- oder Auslaßventils der Bremsanlage nach der Erfindung.Fig. 3 diagrams to illustrate the control of the intake or exhaust valve of the brake system according to the invention.
In Fig. 1 sind lediglich diejenigen Komponenten einer blök- kiergeschützten Bremsanlage wiedergegeben, die zur Erläute¬ rung der Erfindung erforderlich sind. Dargestellt ist der Anschluß einer Radbremse 1 an einen Bremskreis I eines Hauptzylinders 2 einer hydraulischen Bremsanlage. Der Haupt¬ zylinder 2 wird über einen vorgeschalteten Unterdruckver¬ stärker 3 mit Hilfe eines Bremspedals 4 betätigt. Der Druck in der Radbremse 1 wird mit Hilfe eines Einlaßventiles 5 und eines Auslaßventils 6 gesteuert. In ihrer Ruhestellung sind das Einlaßventil 5 auf Durchlaß, das Auslaßventil 6 auf Sperren geschaltet.1 only those components of a block reproduced ski-protected brake system, which are necessary for the explanation of the invention. The connection of a wheel brake 1 to a brake circuit I of a master cylinder 2 of a hydraulic brake system is shown. The master cylinder 2 is actuated by an upstream vacuum booster 3 with the aid of a brake pedal 4. The pressure in the wheel brake 1 is controlled by means of an intake valve 5 and an exhaust valve 6. In their rest position, the inlet valve 5 is switched to passage, the outlet valve 6 to block.
Dargestellt ist hier ein sogen, "geschlossenes" hydrauli¬ sches System. In der Druckabbauphase wird über das Ausla߬ ventil 6 aus der Radbremse 1 das Druckmittel in einen Nie¬ derdruckspeicher 7 geleitet, aus dem es über eine Rückför¬ derpumpe 8 in den Bremskreis I bzw. in den Hauptzylinder 2 zurückgefördert wird.A so-called "closed" hydraulic system is shown here. In the pressure reduction phase, the pressure medium is passed via the outlet valve 6 from the wheel brake 1 into a low-pressure accumulator 7, from which it is fed back via a return pump 8 into the brake circuit I or into the master cylinder 2.
Den Aufbau eines Einlaßventils 5 zeigt Fig. 2. Dargestellt ist hier ein Längsschnitt durch das Ventil. Es besteht im wesentlichen aus einem Ventilanker 9, der in einem Ventil¬ gehäuse 10 axial verschiebbar gelagert ist. Ein Ventilstößel 11 ist Bestandteil dieses Ankers 9. Der Anker 9 mit dem Ven¬ tilstößel 11 wird durch die Kraft einer Schraubenfeder 12 in seiner Ruhelage gehalten, in der eine hydraulische Verbin¬ dung von einem Hydraulikanschluß oder Eingang 13 zu einem Ausgang 14 besteht. Der Anschluß 13 führt zu dem Hauptzylin¬ der 2, der Ausgang 14 zu der Radbremse 1.The structure of an inlet valve 5 is shown in FIG. 2. A longitudinal section through the valve is shown here. It essentially consists of a valve armature 9, which is mounted axially displaceably in a valve housing 10. A valve tappet 11 is part of this armature 9. The armature 9 with the valve tappet 11 is held in its rest position by the force of a coil spring 12, in which there is a hydraulic connection from a hydraulic connection or input 13 to an outlet 14. The connection 13 leads to the main cylinder 2, the outlet 14 to the wheel brake 1.
Das Hydraulikventil 5 nach Fig. 2 besitzt eine Ventilbetäti¬ gungsspule 15 und einen Magnetkern 16. Der Ventilanker 9 und der Magnetkern 16 sind durch einen Luftspalt 17 getrennt, dessen Ausbildung für die Ventil-Charakteristik wesentlich ist. Die elektrischen Ventilanschlüsse sind mit 15a,15b be- zeichnet .The hydraulic valve 5 according to FIG. 2 has a valve actuation coil 15 and a magnetic core 16. The valve armature 9 and the magnetic core 16 are separated by an air gap 17, the design of which is essential for the valve characteristics. The electrical valve connections are 15a, 15b draws.
Bei Ansteuerung des Ventils durch Anlegen einer Spannung an die Ventilspule 15 wird auf den Ventilanker 9 eine Kraft ausgeübt, die zur axialen Verschiebung des Ventilstößels in seine zweite Endposition führt. Der Druckmitteldurchgang von dem Eingang 13 zu Ausgang 14 wird verschlossen.When the valve is actuated by applying a voltage to the valve coil 15, a force is exerted on the valve armature 9, which leads to the axial displacement of the valve tappet into its second end position. The pressure medium passage from the inlet 13 to the outlet 14 is closed.
Die erfindungswesentliche Ansteuerung der Hydraulikventile 5,6 durch Wechselsignale, die nur für die Dauer der Ventil- umschaltung aus der Ruheposition in die zweite Endposition und für die Dauer des Rückschaltvorgangs anliegen, und die Auswirkung dieser Wechselsignale ist den Diagrammen nach Fig. 3 zu entnehmen und wird im folgenden näher erläutert.The control of the hydraulic valves 5, 6 which is essential to the invention by means of alternating signals which are only present for the duration of the valve switchover from the rest position to the second end position and for the duration of the downshifting process, and the effect of these alternating signals can be seen in the diagrams according to FIG. 3 and is explained in more detail below.
Während bisher bekanntlich Hydraulikventile der hier be¬ schriebenen Art durch Anlegen einer Spannung bzw. Ausschal¬ ten umgeschaltet wurden, wobei das entsprechende Signal nach dem Umschalten in die zweite Endposition bis zum Zurück¬ schalten als Dauersignal aufrechterhalten wurde, wird erfin¬ dungsgemäß zum Zeitpunkt t± ein Wechselsignal angelegt. Nach einer vorgegebenen Zeitspanne, in der der Umschaltvorgang beendet sein soll, oder nach der tatsächlichen Umschaltzeit ti ~ t2 geht dann das Wechselsignal in ein Dauersignal über, das das Ventil in der Umschaltstellung bzw. den Ventilstößel in der zweiten Endposition hält. Beim Zurückschalten des Ventils, das zum Zeitpunkt t4 ausgelöst wird, wird wiederum in analoger Weise ein Wechselsignal und anschließend das Dauersignal angelegt.While hydraulic valves of the type described here have hitherto been switched over by applying a voltage or switching off, the corresponding signal being maintained as a permanent signal after switching over to the second end position until switching back, according to the invention at time t ± an alternating signal applied. After a predetermined period of time in which the switchover process is to be ended, or after the actual switchover time ti ~ t 2 , the changeover signal then changes into a continuous signal which holds the valve in the switchover position or the valve tappet in the second end position. When the valve is switched back, which is triggered at time t 4 , an alternating signal is again applied in an analog manner and then the continuous signal.
Die Erfindung beruht auf der Überlegung, daß z.B. bei einem Einlaßventil der in Fig. 2 dargestellten Art beim Anlegen der Spannung an die Spule 15 infolge der SpuleninduktivitätThe invention is based on the consideration that e.g. in an inlet valve of the type shown in Fig. 2 when the voltage is applied to the coil 15 due to the coil inductance
ERSATZBLAπ(REGEL26) und als Folge des bei der Stößelbewegung kleiner werdenden Luftspaltes 17 und des dadurch hervorgerufenen Anstiegs der magnetischen Feldstärke ein "schlagartiges" Schließen des Ventils bzw. Anschlagen des Stößels hervorgerufen wird. Die¬ ses "harte" Anschlagen verursacht die störenden Umschaltge¬ räusche. Beim Zurückschalten des Ventils in die erste Endpo¬ sition oder Ruhelage geschieht Entsprechendes.REPLACEMENT BLAπ (RULE 26) and as a result of the air gap 17 becoming smaller during the tappet movement and the consequent increase in the magnetic field strength, a "sudden" closing of the valve or striking of the tappet is caused. This "hard" striking causes the annoying switching noises. The same happens when the valve is switched back to the first end position or rest position.
Erfindungsgemäß wird daher das Umschalten mit Hilfe des Wechselsignals oder einer Pulsfolge herbeigeführt. Die Stö¬ ßelbewegung wird dadurch verlangsamt. Bei dem Einlaßventil nach Fig. 2 setzt beim Anlegen der Umschaltspannung die Stö¬ ßelbewegung ein. Wird nun die Spannung in der Umschaltphase reduziert - durch abnehmende Spannungsamplitude oder durch eine Pulspause - wird der Stößel durch die Rückstellfeder und durch den Druck im Hydrauliksystem abgebremst. Die er¬ neut ansteigende Spannung oder der folgende Puls erhöhen dann wieder die auf den Stößel einwirkende Kraft in Schlie߬ richtung. Auf diese Weise erfolgt durch das Wechselsignal ein schrittweises, insgesamt verzögertes Schließen oder Öff¬ nen des Ventil und ein relativ "sanftes" Anschlagen in den Endpositionen. Die gestellte Aufgabe, die Ventilgeräusche entscheidend zu verringern, wird auf diese Weise gelöst. In der oberen Kurve 'A' in Fig. 3 ist der 'Sollwert' der Ventilposition wiedergegeben. Zum Zeitpunkt ti steht fest, daß das Ventil umschalten soll, zum Zeitpunkt t4 beginnt das Zurückschalten.According to the invention, the switching is therefore brought about with the aid of the alternating signal or a pulse sequence. The ram movement is thereby slowed down. In the inlet valve according to FIG. 2, the tappet movement starts when the switching voltage is applied. If the tension is reduced in the changeover phase - due to a decreasing tension amplitude or a pulse pause - the ram is braked by the return spring and by the pressure in the hydraulic system. The newly increasing voltage or the following pulse then again increase the force acting on the plunger in the closing direction. In this way, the alternating signal results in a gradual, overall delayed closing or opening of the valve and a relatively "gentle" stop in the end positions. The task of reducing valve noise significantly is solved in this way. In the upper curve 'A' in Fig. 3, the 'setpoint' of the valve position is shown. At time ti it is clear that the valve should switch over, at time t 4 the downshift begins.
Den erfindungsgemäß vorgegebenenVerlauf der an der Spule angelegten Spannung zeigt das Diagramm 'B' in Fig. 3. In der Umschaltphase tj - t2 liegt ein Wechselsignal, hier ein puls- förmiges Wechselsignal an, das zum Zeitpunkt t2, wenn der Schließvorgang beendet ist, in ein Dauersignal übergeht. In analoger Weise erfolgt das Zurückschalten; in der Zeitspanne t4 bis t5 liegen wiederum Pulse an.Diagram 'B' in FIG. 3 shows the course of the voltage applied to the coil as specified in accordance with the invention. In the switching phase tj-t 2 there is an alternating signal, here a pulsed alternating signal, which occurs at time t 2 when the closing process has ended , changes to a continuous signal. In the downshift takes place in an analogous manner; pulses are again present in the time period t 4 to t 5 .
Den durch den Spannungsverlauf nach 'B' hervorgerufenen Ver¬ lauf des Stromes durch die Spule 15 (Fig. 2) und den Verlauf der magnetischen Feldstärke zeigen die Diagramme 'C und 'D' in Fig. 3. Die Stromänderung durch das Wechselsignal ist erst zum Zeitpunkt t3 bzw. t6 beendet.The diagrams' C and 'D' in Fig. 3 show the course of the current through the coil 15 (FIG. 2) and the course of the magnetic field strength caused by the voltage course according to 'B'. The change in current due to the alternating signal is only first ended at time t 3 or t 6 .
Schließlich ist in dem Diagramm 'E' der Fig. 3 noch der Ven¬ tilweg oder Stößelweg aufgetragen. Es ist ersichtlich, daß durch den Einfluß des Wechselsignals eine wesentliche Ver¬ langsamung der Ventilstößelbewegung erreicht wird; die Zeit¬ spannen tj bis t2 und t4 bis t5 sind notwendig, um den Ven¬ tilstößel von der einen Endposition in die andere Endposi¬ tion zu überführen. Finally, the valve path or ram path is plotted in diagram 'E' in FIG. 3. It can be seen that the influence of the alternating signal results in a substantial slowdown of the valve tappet movement; the time spans tj to t 2 and t 4 to t 5 are necessary in order to transfer the valve tappet from one end position to the other end position.

Claims

Patentansprüche claims
1. Hydraulische Bremsanlage mit elektrisch umschaltbaren Hydraulikventilen, die zur Modulation des Bremsdruckes in den Radbremsen zwecks BlockierSchutzregelung, An¬ triebsschlupfregelung oder dergl. vorgesehen sind, da¬ durch gekennzeichnet, daß zur Umschaltung der Hydraulik¬ ventile (5,6) von der einen in die andere Endstellung für die Dauer der Umschaltung (ti - t2; t4 - t5) ein1. Hydraulic brake system with electrically switchable hydraulic valves, which are provided for modulating the brake pressure in the wheel brakes for the purpose of anti-lock control, traction control or the like, characterized in that for switching the hydraulic valves (5, 6) from one into the other end position for the duration of the switchover (ti - t 2 ; t 4 - t 5 )
Wechselsignal angelegt wird, das den Umschaltvorgang im Vergleich zu einem "Ein- bzw. Ausschalten" des Hydrau¬ likventils (5,6) verzögert, und daß nach dem Umschalten oder nach einer vorgegebenen Umschaltzeitdauer ein Dau¬ ersignal an dem Hydraulikventil anliegt.Alternating signal is applied, which delays the switching process compared to "switching on or off" the hydraulic valve (5, 6), and that after the switching or after a predetermined switching time, a permanent signal is present at the hydraulic valve.
2. Bremsanlage nach Anspruch 1, dadurch gekennzeichnet, daß das Wechselsignal eine Pulsfolge ist, deren Frequenz hoch bzw. deren Pulszeiten und Pulspausen kurz im Ver¬ gleich zu der für den Umschaltvorgang benötigten Zeit¬ dauer sind. 2. Brake system according to claim 1, characterized in that the alternating signal is a pulse sequence, the frequency of which is high or whose pulse times and pulse pauses are short in comparison to the time duration required for the switching process.
PCT/EP1996/002687 1995-07-08 1996-06-20 Hydraulic braking system with electrically switched hydraulic valves WO1997002970A1 (en)

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DE19524952.6 1995-07-08

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EP0982207A3 (en) * 1998-08-28 2001-04-25 Toyota Jidosha Kabushiki Kaisha Apparatus for increasing brake cylinder pressure by controlling pump motor and reducing the pressure by controlling electric energy applied to control valve
WO2005051740A1 (en) * 2003-11-26 2005-06-09 Robert Bosch Gmbh Method for controlling a two-stage selector valve
WO2007141294A1 (en) 2006-06-06 2007-12-13 Continental Teves Ag & Co. Ohg Method for activating hydraulic inlet valves which are activated in an analog fashion
CN100377940C (en) * 2003-11-26 2008-04-02 罗伯特·博世有限公司 Method for controlling a two-stage selector valve
US20130147260A1 (en) * 2010-05-27 2013-06-13 Continental Teve AG & Co. oHG Method for Controlling the Pressure in an Electronically Controlled Hydraulic Brake System for a Motor Vehicle

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JP3379397B2 (en) * 1997-08-12 2003-02-24 トヨタ自動車株式会社 Hydraulic brake device
JP3768685B2 (en) 1998-07-01 2006-04-19 株式会社日立製作所 Brake fluid pressure control device
JP5411118B2 (en) 2010-12-23 2014-02-12 本田技研工業株式会社 Brake device for vehicle

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Publication number Priority date Publication date Assignee Title
EP0982207A3 (en) * 1998-08-28 2001-04-25 Toyota Jidosha Kabushiki Kaisha Apparatus for increasing brake cylinder pressure by controlling pump motor and reducing the pressure by controlling electric energy applied to control valve
US6913326B1 (en) 1998-08-28 2005-07-05 Toyota Jidosha Kabushiki Kaisha Apparatus for increasing brake cylinder pressure by controlling pump motor and reducing the pressure by controlling electric energy applied to control valve
WO2005051740A1 (en) * 2003-11-26 2005-06-09 Robert Bosch Gmbh Method for controlling a two-stage selector valve
CN100377940C (en) * 2003-11-26 2008-04-02 罗伯特·博世有限公司 Method for controlling a two-stage selector valve
US7992947B2 (en) 2003-11-26 2011-08-09 Robert Bosch Gmbh Method for activating a two-stage switching valve
WO2007141294A1 (en) 2006-06-06 2007-12-13 Continental Teves Ag & Co. Ohg Method for activating hydraulic inlet valves which are activated in an analog fashion
US20130147260A1 (en) * 2010-05-27 2013-06-13 Continental Teve AG & Co. oHG Method for Controlling the Pressure in an Electronically Controlled Hydraulic Brake System for a Motor Vehicle
JP2013531572A (en) * 2010-05-27 2013-08-08 コンティネンタル・テーベス・アクチエンゲゼルシヤフト・ウント・コンパニー・オッフェネ・ハンデルスゲゼルシヤフト Method for controlling pressure in a hydraulic system, in particular an electronically regulated brake system for an automobile
KR101765446B1 (en) * 2010-05-27 2017-08-07 콘티넨탈 테베스 아게 운트 코. 오하게 Method for controlling the pressure in an electronically controlled hydraulic brake system for a motor vehicle

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