WO1994029149A1 - Slip-controlled hydraulic brake system - Google Patents

Slip-controlled hydraulic brake system Download PDF

Info

Publication number
WO1994029149A1
WO1994029149A1 PCT/EP1994/001517 EP9401517W WO9429149A1 WO 1994029149 A1 WO1994029149 A1 WO 1994029149A1 EP 9401517 W EP9401517 W EP 9401517W WO 9429149 A1 WO9429149 A1 WO 9429149A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure
brake
valve
line
low
Prior art date
Application number
PCT/EP1994/001517
Other languages
German (de)
French (fr)
Inventor
Erhard Beck
Peter Volz
Jochen Burgdorf
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 WO1994029149A1 publication Critical patent/WO1994029149A1/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
    • B60T8/48—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 connecting the brake actuator to an alternative or additional source of fluid pressure, e.g. traction control systems
    • B60T8/4809—Traction control, stability control, using both the wheel brakes and other automatic braking systems
    • B60T8/4827—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems
    • B60T8/4863—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems
    • B60T8/4872—Traction control, stability control, using both the wheel brakes and other automatic braking systems in hydraulic brake systems closed systems 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
    • B60T8/341—Systems characterised by their valves

Definitions

  • the present invention is based on a slip-controlled hydraulic brake system according to the preamble of the main claim.
  • a generic brake system is known from DE 41 08 756 AI.
  • the brake system described therein works in the brake slip control according to the known return principle.
  • the second suction line was installed, in which a hydraulically operated, pressure-free switch valve is inserted.
  • the pump sucks pressure medium through the master cylinder out of the trailing tank via this switchover valve. So that the pressure medium conveyed by the pump reaches the wheel brake cylinder and does not flow through the brake line via the master brake cylinder back into the follow-up tank, there is between the connection point of the second suction line and the confluence of the pressure line into the Brake line an electromagnetically operated separation valve is used. This remains closed during traction control.
  • the hydraulically operated changeover valve is closed by the master cylinder pressure during each pedal-operated braking, that is to say with every normal braking and during a brake slip control.
  • the changeover valve In practice, however, it has proven to be expedient for the changeover valve to close under normal roadway conditions, that is to say with a high coefficient of friction, only when the brake pressure is approximately 5 to 10 bar. This eliminates unnecessary switching noises for light, uncritical braking. The situation is different when braking on a road with a low coefficient of friction. With black ice, for example, even low braking pressures lead to the wheels locking. A permanent reduction in brake pressure is not possible when the changeover valve is open because the lowest achievable brake pressure when the changeover valve is open is equal to the master cylinder pressure as soon as the low-pressure accumulator is filled.
  • the object of the present invention is therefore to equip a generic brake system with a changeover valve, which does not close with every pedal-operated braking, but nevertheless ensures a reliable function of the brake slip control even with low road friction values.
  • the principle of the invention thus exists in closing the hydraulically operated changeover valve depending on the filling state of the low-pressure accumulator.
  • the pressure in the master brake cylinder can additionally act in the closing direction, it depending on the design of the changeover valve whether it is able to close the valve at a certain pressure or only has a closing support effect when the valve is closed.
  • the changeover valve can be controlled by the low-pressure accumulator depending on the path or pressure.
  • the piston which delimits the low-pressure accumulator and is acted upon by compression springs can act at least indirectly on the valve closing member due to its stroke.
  • Fig. 2 further versions of the hydraulic to actuated changeover valve of a Fig. 4 brake system according to the invention.
  • 1 has a master brake cylinder 1 which is connected to an overflow tank 2 and from which the brake line 3 leads via the isolating valve 13 and the inlet valve 4 to the wheel brake cylinder 6 of a driven wheel.
  • the outlet valve 5 is arranged in the return line 12, which leads to the low-pressure accumulator 9. This is connected via the first suction line 7 to the suction side of the self-priming pump 10, which has a second suction line which branches off from the brake line 3.
  • the pressure line 11 of the pump 10 leads to the brake line 3 at a location between the isolating valve 13 and the inlet valve 4th
  • the hydraulically operated, pressurelessly open changeover valve 14 is inserted into the second suction line 8.
  • the changeover valve 14 has essentially five different chambers 16 to 20.
  • the inlet chamber 17 can be separated from the outlet chamber 16 by applying the closing member 21 to the valve seat 22.
  • the closing member 21 is arranged in the inlet space 17, which is connected to the master cylinder 1.
  • a valve tappet 23 runs from the closing member 21 through the valve seat 22 and the outlet space 16 to a membrane 24 which separates the outlet space 16 from the atmospheric pressure.
  • the membrane 24 is acted upon by the force of a compression spring 25 toward the valve seat 22. Their bias is greater than that in the inlet space 16th arranged, acting in the opposite direction compression spring 26. In the depressurized state, the changeover valve 14 is thus open.
  • the pump 10 can draw in pressure medium from the secondary tank 2 through the second suction line via the outlet chamber 16, the inlet chamber 17 and the master brake cylinder 1 when traction control is required.
  • the switching valve 14 is also acted upon by the pressure in the low-pressure accumulator 9 in the closing direction.
  • the low-pressure accumulator 9 is connected to the accumulator pressure chamber 19 via the control line 5.
  • the pressure in the accumulator pressure chamber 19 acts on the stepped piston 27 in the direction of the valve closing member 21.
  • the stepped piston 27 is loaded by the compression spring 28 against the low pressure accumulator pressure and sealed with a small diameter into the inlet space 17, where it rests on the closing member 21.
  • the stepped piston 27 is guided on the side facing away from the closing member with the same diameter as in the inlet chamber 17 and into the compensation chamber 20, where it is also exposed to the master cylinder pressure. Since the sealed surface of the stepped piston 27, which the accumulator pressure chamber 19 from the spring chamber 18 separates, is larger than the diameter in each case into the chambers 17 and 20 acted upon by the master cylinder pressure, the low-pressure accumulator 9 has an active surface in the direction of the closing member 21, so that the low-pressure accumulator pressure acts in the closing direction of the changeover valve 14. For this purpose, the spring chamber 18 is connected to the atmosphere.
  • the low-pressure accumulator is already integrated in the valve housing.
  • the low-pressure accumulator 9 from FIG. 1 can therefore be omitted. Otherwise, the circuit diagram of FIG. 1 can be adopted completely for FIGS. 2 and 3.
  • the changeover valve 114 shown in FIG. 2 differs from the changeover valve 14 from FIG. 2 only in the construction of the stepped piston 127.
  • This has an axial bore 129 which connects the inlet chamber 117 to the compensating chamber 120.
  • a shackled compression spring 130 Arranged within the bore 129 is a shackled compression spring 130 which holds the pin 131 guided through the bore 129 into the inlet space 117 against a step of the bore 129 on the inlet space side as seen from the compression spring 130.
  • the spring hardness of the compression spring 130 is greater than that of the compression spring 125 acting in the opening direction.
  • the embodiment according to FIG. 2 has the advantage that, when the closing member 121 is in contact with the valve seat 122, the stepped piston 127 is shifted even further into the inlet space 117 can be. An additional storage volume is therefore also available when the switching valve 114 is closed, so that a separate low-pressure storage can be omitted in this embodiment.
  • FIG. 3 differs from that of FIG. 2 in the arrangement of the valve itself.
  • the pin 231 is rigidly connected to the closing member 221, so that the changeover valve 214 is connected by the driver connection between step piston 227 and pin 231 is always open when the pressure chamber 219 is depressurized.
  • the master brake cylinder pressure has no effective surface in the valve closing direction as long as the closing member 221 is lifted off the valve seat 222. Only when the valve is closed, that is to say when the closing member 221 bears against the valve seat 222, does the pressure from the master brake cylinder assist in closing.
  • valves from FIG. 1 and FIG. 2 can be opened by a suction of the pump during a drive closing control even when the low-pressure slip is filled, because the atmospheric pressure outside the membrane at negative pressure in the Exhaust chamber acts opening, the switching valve 214 is switched only by the stroke of the stepped piston 227.
  • the valve can only close when a sufficient control volume is available in the storage pressure chamber 219.
  • FIG. 4 shows a particularly short version of a changeover valve 314, in which, however, as in FIG. 1, a separate low-pressure accumulator is required. Since the pressure medium connections present here are not congruent with those of the previous exemplary embodiments, the lines leading to the connections have been provided with the corresponding reference symbols according to FIG. 1.
  • the valve tappet 323 merges with the diaphragm 324 into a piston 332, which is sealingly guided into the accumulator pressure chamber 319.
  • the piston 332 has a rigid connection to the membrane 324. While the pressure in the low-pressure accumulator is the effective area in the closing direction of the changeover valve Differential area from the membrane area and the cross section of the piston 332, the pressure in the master brake cylinder only acts on the cross-sectional area of the piston 332 when the valve is open.
  • this cross-sectional area of the piston 232 is smaller than the area on the valve seat 321 covered by the closing member 321 , as in the example above, the pump is unable to open the valve when the low-pressure accumulator is full, ie the accumulator pressure chamber 319 is under pressure. This is not necessary for the reasons described above.

Abstract

The present invention relates to an anti-lock drive slip controlled brake system operating in anti-lock mode on the recirculation principle and fitted with a self-priming pump. For drive slip control, the pump (10) takes in pressure medium through the brake master cylinder (1) from the after-container (2). A hydraulically operated changeover valve (14) is fitted in the intake line (8) between the intake side of the pump (10) and the master cylinder (1). To prevent said changeover valve (14) from closing at any, even very light, pressure on the foot-brake, its changeover depends on the pressure in the low-pressure reservoir (9). Thus the changeover valve (14) is always closed when the low-pressure reservoir (9) is full. The valve can also be actuated by the pressure in the master cylinder. Changeover can take place, however, at braking pressures of over 5 bar.

Description

Schlupfgeregelte hydraulische BremsanlageSlip-controlled hydraulic brake system
Die vorliegende Erfindung geht aus von einer schlupf¬ geregelten hydraulichen Bremsanlage gemäß dem Ober¬ begriff des Hauptanspruches.The present invention is based on a slip-controlled hydraulic brake system according to the preamble of the main claim.
Eine gattungsgemäße Bremsanlage ist aus der DE- 41 08 756 AI bekannt. Die darin beschriebene Bremsan¬ lage arbeitet bei der Bremsschlupfregelung nach dem bekannten Rückförderprinzip. Für die Antriebsschlupf- regelung wurde die zweite Saugleitung installiert, in welche ein hydraulisch betätigtes, drucklos offenes Umschaltventil eingesetzt ist. Über dieses Umschalt¬ ventil saugt die Pumpe zu Beginn einer Antriebs¬ schlupfregelung Druckmittel durch den Hauptzylinder aus dem Nachlaufbehälter. Damit das von der Pumpe geförderte Druckmittel zum Radbresmzylinder gelangt und nicht durch die Bremsleitung über den Hauptbrems¬ zylinder zurück in den Nachlaufbehälter fließt, ist zwischen der Anschlußstelle der zweiten Saugleitung und der Einmündung der Druckleitung in die Bremsleitung ein elektromagnetisch betätigtes Trenn¬ ventil eingesetzt. Dieses bleibt während einer An¬ triebsschlupfregelung geschlossen. Das hydraulisch betätigte Umschaltventil dagegen wird bei jeder pedal¬ betätigten Bremsung, also bei jeder Normalbremsung sowie während einer Bremsschlupfrgelung vom Haupt¬ zylinderdruck geschlossen.A generic brake system is known from DE 41 08 756 AI. The brake system described therein works in the brake slip control according to the known return principle. For the traction control, the second suction line was installed, in which a hydraulically operated, pressure-free switch valve is inserted. At the start of a traction control system, the pump sucks pressure medium through the master cylinder out of the trailing tank via this switchover valve. So that the pressure medium conveyed by the pump reaches the wheel brake cylinder and does not flow through the brake line via the master brake cylinder back into the follow-up tank, there is between the connection point of the second suction line and the confluence of the pressure line into the Brake line an electromagnetically operated separation valve is used. This remains closed during traction control. The hydraulically operated changeover valve, on the other hand, is closed by the master cylinder pressure during each pedal-operated braking, that is to say with every normal braking and during a brake slip control.
In der Praxis hat es sich jedoch als zweckmäßig er¬ wiesen, daß das Umschaltventil unter normalen Fahr¬ bahnbedingungen, also bei hohem Reibwert, sich erst bei einem Bremsdruck von etwa 5 bis 10 bar schließt. Dadurch entfallen bei leichten, unkritischen Bremsungen unnötige Schaltgeräusche. Anders sieht es bei Bremsungen auf einer Fahrbahn mit niedrigem Reib¬ wert aus. Bei Glatteis beispielweise führen schon geringe Bremsdrücke zum Blockieren der Räder. Ein dauerhafter Bremsdruckabbau ist aber bei geöffnetem Umschaltventil nicht möglich, weil der niedrigste erreichbare Bremsdruck bei geöffnetem Umschaltventil gleich dem Hauptzylinderdruck ist, sobald der Nieder¬ druckspeicher gefüllt ist.In practice, however, it has proven to be expedient for the changeover valve to close under normal roadway conditions, that is to say with a high coefficient of friction, only when the brake pressure is approximately 5 to 10 bar. This eliminates unnecessary switching noises for light, uncritical braking. The situation is different when braking on a road with a low coefficient of friction. With black ice, for example, even low braking pressures lead to the wheels locking. A permanent reduction in brake pressure is not possible when the changeover valve is open because the lowest achievable brake pressure when the changeover valve is open is equal to the master cylinder pressure as soon as the low-pressure accumulator is filled.
Die Aufgabe der vorliegenden Erfindung liegt also darin, eine gattungsgemäße Bremsanlage mit einem Umschaltventil auszurüsten, welches zwar nicht bei jeder pedalbetätigten Bremsung schließt, jedoch trotz¬ dem auch bei niedrigen Fahrbahnreibwerten eine sichere Funktion der Bremsschlupfregelung gewährleistet. Das Prinzip der Erfindung besteht also darin, das hydraulisch betätigte Umschaltventil ab¬ hängig vom Füllzustand des Niederdruckspeichers zu schließen. Der Druck im Hauptbremszylinder kann dabei zusätzlich in Schließrichtung wirken, wobei es von der Auslegung des Umschaltventils abhängt, ob er in der Lage ist, das Ventil bei einem bestimmten Druck zu schließen oder nur bei geschlossenem Ventil schlie߬ unterstützend wirkt. Die Steuerung des Umschaltventils durch den Niederdruckspeicher kann wegabhängig oder druckabhängig erfolgen.The object of the present invention is therefore to equip a generic brake system with a changeover valve, which does not close with every pedal-operated braking, but nevertheless ensures a reliable function of the brake slip control even with low road friction values. The principle of the invention thus exists in closing the hydraulically operated changeover valve depending on the filling state of the low-pressure accumulator. The pressure in the master brake cylinder can additionally act in the closing direction, it depending on the design of the changeover valve whether it is able to close the valve at a certain pressure or only has a closing support effect when the valve is closed. The changeover valve can be controlled by the low-pressure accumulator depending on the path or pressure.
Besonders platzsparend ist eine Unterbringung des Niederdruckspeichers und des Umschaltventils in dem¬ selben Gehäuse. Dadurch kann der den Niederdruck¬ speicher begrenzende, druckfederbeaufschlagte Kolben durch seinen Hub zumindest mittelbar das Ventil¬ schließglied beaufschlagen.It is particularly space-saving to accommodate the low-pressure accumulator and the changeover valve in the same housing. As a result, the piston which delimits the low-pressure accumulator and is acted upon by compression springs can act at least indirectly on the valve closing member due to its stroke.
Weitere Vorteile ergeben sich aus den übrigen Unteran¬ sprüchen, sowie aus der nun folgenden weiteren Er¬ läuterung des Erfindungsgedankens anhand der Be¬ schreibung von vier Figuren.Further advantages result from the other subclaims, and from the further explanation of the inventive concept that follows, based on the description of four figures.
Es zeigen:Show it:
Fig. 1 eine erfindungsgemäße Bremsanlage;1 shows a brake system according to the invention;
Fig. 2 weitere Ausführungen des hydraulisch bis betätigten Umschaltventils einer Fig. 4 erfindugsgemäßen Bremsanlage. Die Bremsanlage nach Fig. 1 besitzt einen Hauptbrems¬ zylinder 1, welcher an einen Nachlaufbehälter 2 ange¬ schlossen ist und von welchem die Bremsleitung 3 über das Trennventil 13 und das Einlaßventil 4 zum Rad¬ bremszylinder 6 eines angetriebenen Rades führt. Das Auslaßventil 5 ist in der Rücklaufleitung 12 ange¬ ordnet, welche zum Niederdruckspeicher 9 führt. Dieser ist über die erste Saugleitung 7 an die Saugseite der selbstansaugenden Pumpe 10 angeschlossen, die eine zweite Saugleitung besitzt, welche von der Brems¬ leitung 3 abzweigt. Die Druckleitung 11 der Pumpe 10 führt zur Bremsleitung 3 an eine Stelle zwischen dem Trennventil 13 und dem Einlaßventil 4.Fig. 2 further versions of the hydraulic to actuated changeover valve of a Fig. 4 brake system according to the invention. 1 has a master brake cylinder 1 which is connected to an overflow tank 2 and from which the brake line 3 leads via the isolating valve 13 and the inlet valve 4 to the wheel brake cylinder 6 of a driven wheel. The outlet valve 5 is arranged in the return line 12, which leads to the low-pressure accumulator 9. This is connected via the first suction line 7 to the suction side of the self-priming pump 10, which has a second suction line which branches off from the brake line 3. The pressure line 11 of the pump 10 leads to the brake line 3 at a location between the isolating valve 13 and the inlet valve 4th
In die zweite Saugleitung 8 ist das hydraulisch be¬ tätigte, drucklos offene Umschaltventil 14 eingefügt.The hydraulically operated, pressurelessly open changeover valve 14 is inserted into the second suction line 8.
Das Umschaltventil 14 weist im wesentlichen fünf verschiedene Kammern 16 bis 20 auf. Die Einlaßkammer 17 ist von der Auslaßkammer 16 durch Anlegen des Schließgliedes 21 an den Ventilsitz 22 trennbar. Das Schließglied 21 ist im Einlaßraum 17 angeordnet, welcher an den Hauptbremszylinder 1 angeschlossen ist. Vom Schließglied 21 verläuft ein Ventilstößel 23 durch den Ventilsitz 22 und den Auslaßraum 16 zu einer Membran 24, welche den Auslaßraum 16 vom Atmosphären¬ druck trennt. Die Membran 24 ist zum Ventilsitz 22 hin von der Kraft einer Druckfeder 25 beaufschlagt. Deren Vorspannung ist größer als die der im Einlaßraum 16 angeordneten, in Gegenrichtung wirkenden Druckfeder 26. In drucklosem Zustand ist das Umschaltventil 14 also geöffnet. Die Pumpe 10 kann durch die zweite Saugleitung über die Auslaßkammer 16, die Einlaßkammer 17 und den Hauptbremszylinder 1 Druckmittel aus dem Nachlaufbehälter 2 ansaugen, wenn eine Antriebs¬ schlupfregelung erforderlich ist.The changeover valve 14 has essentially five different chambers 16 to 20. The inlet chamber 17 can be separated from the outlet chamber 16 by applying the closing member 21 to the valve seat 22. The closing member 21 is arranged in the inlet space 17, which is connected to the master cylinder 1. A valve tappet 23 runs from the closing member 21 through the valve seat 22 and the outlet space 16 to a membrane 24 which separates the outlet space 16 from the atmospheric pressure. The membrane 24 is acted upon by the force of a compression spring 25 toward the valve seat 22. Their bias is greater than that in the inlet space 16th arranged, acting in the opposite direction compression spring 26. In the depressurized state, the changeover valve 14 is thus open. The pump 10 can draw in pressure medium from the secondary tank 2 through the second suction line via the outlet chamber 16, the inlet chamber 17 and the master brake cylinder 1 when traction control is required.
Außer vom Hauptbremszylinderdruck, welcher bei ge¬ öffnetem Umschaltventil 14 auf die Membran 24 und bei geschlossenem Umschaltventil 14 auf das Schließglied 21 jeweils in Schließrichtung wirkt, wird das Um¬ schaltventil 14 auch noch vom Druck im Niederdruck¬ speicher 9 in Schließrichtung beaufschlagt. Dazu ist der Niederdruckspeicher 9 über die Steuerleitung 5 an die Speicherdruckkammer 19 angeschlossen. Der Druck in der Speicherdruckkammer 19 wirkt auf den Stufenkolben 27 in Richtung auf das Ventilschließglied 21. Der Stufenkolben 27 ist von der Druckfeder 28 gegen den Niederdruckspeicherdruck belastet und mit einem kleinen Durchmesser abgedichtet in den Einlaßraum 17 geführt, wo er am Schließglied 21 anliegt. Damit der Hauptbremszylinderdruck keine unerwünschten Aus¬ wirkungen auf den Niederdruckspeicher 9 hat, ist der Stufenkolben 27 auf der dem Schließglied abgewandten Seite mit gleichem Durchmesser wie in die Einlaßkammer 17 auch in die Ausgleichskammer 20 geführt, wo er ebenfalls dem Hauptbremszylinderdruck ausgesetzt ist. Da die abgedichtete Fläche des Stufenkolbens 27, welche die Speicherdruckkammer 19 von der Federkammer 18 trennt, größer ist als die jeweils in die vom Hauptbremszylinderdruck beaufschlagten Kammern 17 und 20 geführten Durchmesser, besitzt der Niederdruck¬ speicher 9 eine Wirkfläche in Richtung auf das Schließglied 21, so daß der Niederdruckspeicherdruck in Schließrichtung des Umschaltventils 14 wirkt. Die Federkammer 18 ist dazu an die Atmosphäre ange¬ schlossen.In addition to the master cylinder pressure, which acts on the diaphragm 24 when the switching valve 14 is open and on the closing element 21 when the switching valve 14 is closed, the switching valve 14 is also acted upon by the pressure in the low-pressure accumulator 9 in the closing direction. For this purpose, the low-pressure accumulator 9 is connected to the accumulator pressure chamber 19 via the control line 5. The pressure in the accumulator pressure chamber 19 acts on the stepped piston 27 in the direction of the valve closing member 21. The stepped piston 27 is loaded by the compression spring 28 against the low pressure accumulator pressure and sealed with a small diameter into the inlet space 17, where it rests on the closing member 21. So that the master cylinder pressure does not have any undesirable effects on the low-pressure accumulator 9, the stepped piston 27 is guided on the side facing away from the closing member with the same diameter as in the inlet chamber 17 and into the compensation chamber 20, where it is also exposed to the master cylinder pressure. Since the sealed surface of the stepped piston 27, which the accumulator pressure chamber 19 from the spring chamber 18 separates, is larger than the diameter in each case into the chambers 17 and 20 acted upon by the master cylinder pressure, the low-pressure accumulator 9 has an active surface in the direction of the closing member 21, so that the low-pressure accumulator pressure acts in the closing direction of the changeover valve 14. For this purpose, the spring chamber 18 is connected to the atmosphere.
In den Fig. 2 und 3 ist der Niederdruckspeicher schon in das Ventilgehäuse integriert. Der Niederdruck¬ speicher 9 aus Fig. 1 kann also entfallen. Ansonsten kann das Schaltbild von Fig. 1 vollständig für die Fig. 2 und 3 übernommen werden.2 and 3, the low-pressure accumulator is already integrated in the valve housing. The low-pressure accumulator 9 from FIG. 1 can therefore be omitted. Otherwise, the circuit diagram of FIG. 1 can be adopted completely for FIGS. 2 and 3.
Das in Fig. 2 dargestellte Umschaltventil 114 unter¬ scheidet sich von dem Umschaltventil 14 aus Fig. 2 nur durch den Aufbau des Stufenkolbens 127. Dieser besitzt eine axiale Bohrung 129, welche die Einlaßkammer 117 mit der Ausgleichskammer 120 verbindet. Innerhalb der Bohrung 129 ist eine gefesselte Druckfeder 130 ange¬ ordnet, welche den durch die Bohrung 129 in den Ein¬ laßraum 117 geführten Stift 131 an einer von der Druckfeder 130 aus gesehen einlaßraumseitigen Stufe der Bohrung 129 im Anschlag hält. Die Federhärte der Druckfeder 130 ist dabei größer als die der in Öffnungsrichtung wirkenden Druckfeder 125.The changeover valve 114 shown in FIG. 2 differs from the changeover valve 14 from FIG. 2 only in the construction of the stepped piston 127. This has an axial bore 129 which connects the inlet chamber 117 to the compensating chamber 120. Arranged within the bore 129 is a shackled compression spring 130 which holds the pin 131 guided through the bore 129 into the inlet space 117 against a step of the bore 129 on the inlet space side as seen from the compression spring 130. The spring hardness of the compression spring 130 is greater than that of the compression spring 125 acting in the opening direction.
Sobald sich die als Niederdruckspeicher dienende Speicherdruckkammer 119 mit Druckmittel füllt und der Stufenkolben 127 zum Schließglied 121 hin verschoben wird, drückt der Stift 131 das Schließglied 121 gegen den Ventilsitz 122. Gegenüber Fig. 1 hat die Aus¬ führungsform nach Fig. 2 den Vorteil, daß auch bei Anlage des Schließgliedes 121 am Ventilsitz 122 der Stufenkolben 127 noch weiter in den Einlaßraum 117 verschoben werden kann. Es steht also auch bei ge¬ schlossenem Umschaltventil 114 noch ein zusätzliches Speichervolumen zur Verfügung, so daß ein separater Niederdruckspeicher bei dieser Ausführungsform ent¬ fallen kann.As soon as the accumulator pressure chamber 119 serving as a low-pressure accumulator fills with pressure medium and the stepped piston 127 is displaced towards the closing element 121 the pin 131 presses the closing member 121 against the valve seat 122. Compared to FIG. 1, the embodiment according to FIG. 2 has the advantage that, when the closing member 121 is in contact with the valve seat 122, the stepped piston 127 is shifted even further into the inlet space 117 can be. An additional storage volume is therefore also available when the switching valve 114 is closed, so that a separate low-pressure storage can be omitted in this embodiment.
Dasselbe gilt für Fig. 3. Das hier dargestellte Aus¬ führungsbeispiel unterscheidet sich von dem aus Fig. 2 in der Anordnung des Ventils selbst. Hier ist der Stift 231 starr mit dem Schließglied 221 verbunden, so daß das Umschaltventil 214 durch die Mitnehmerverbin¬ dung zwischen Stufenkolben 227 und Stift 231 bei druckloser Speicherdruckkammer 219 stets geöffnet ist. Im Gegensatz zu den vorher beschriebenen Beispielen besitzt beim Umschaltventil 214 nach Fig. 3 der Haupt¬ bremszylinderdruck keine Wirkfläche in Ventilschlie߬ richtung, solange das Schließglied 221 vom Ventilsitz 222 abgehoben ist. Lediglich bei geschlossenem Ventil, also bei Anlage des Schließgliedes 221 am Ventilsitz 222 wirkt der Druck vom Hauptbremszylinder her schließunterstützend.The same applies to FIG. 3. The exemplary embodiment shown here differs from that of FIG. 2 in the arrangement of the valve itself. Here, the pin 231 is rigidly connected to the closing member 221, so that the changeover valve 214 is connected by the driver connection between step piston 227 and pin 231 is always open when the pressure chamber 219 is depressurized. In contrast to the previously described examples, in the changeover valve 214 according to FIG. 3, the master brake cylinder pressure has no effective surface in the valve closing direction as long as the closing member 221 is lifted off the valve seat 222. Only when the valve is closed, that is to say when the closing member 221 bears against the valve seat 222, does the pressure from the master brake cylinder assist in closing.
Während die Ventile aus Fig. 1 und Fig. 2 während einer Antriebsschließregelung auch bei gefülltem Niederdruckschlupfs durch das Ansaugen der Pumpe geöffnet werden können, weil der Atmosphärendruck außerhalb der Membran bei Unterdruck in der Auslaßkammer öffnend wirkt, ist das Umschaltventil 214 allein um den Hub des Stufenkolbens 227 schaltbar. Es ergeben sich jedoch auch bei Antriebsschlupf¬ regelung keine Probleme, da sich das Ventil erst dann schließen kann, wenn ein ausreichendes Regelvolumen in der Speicherdruckkammer 219 zur Verfügung steht.While the valves from FIG. 1 and FIG. 2 can be opened by a suction of the pump during a drive closing control even when the low-pressure slip is filled, because the atmospheric pressure outside the membrane at negative pressure in the Exhaust chamber acts opening, the switching valve 214 is switched only by the stroke of the stepped piston 227. However, there are also no problems with traction control, since the valve can only close when a sufficient control volume is available in the storage pressure chamber 219.
Fig. 4 zeigt eine besonders kurzbauende Version, eines Umschaltventils 314, bei welchem jedoch wie in Fig. 1 ein separater Niederdruckspeicher benötigt wird. Da die hier vorhandenen Druckmittelanschlüsse nicht deckungsgleich mit denen der vorhergehenden Aus- führungsbeispiele sind, wurden die zu den Anschlüssen führenden Leitungen mit den entsprechenden Bezugs¬ zeichen nach Fig. 1 versehen.FIG. 4 shows a particularly short version of a changeover valve 314, in which, however, as in FIG. 1, a separate low-pressure accumulator is required. Since the pressure medium connections present here are not congruent with those of the previous exemplary embodiments, the lines leading to the connections have been provided with the corresponding reference symbols according to FIG. 1.
Zur Baulängenverkürzung trägt hauptsächlich die Tat¬ sache bei, daß die Speicherdruckkammer 319 an der Membran 324 angeordnet ist, auf welche in den Aus¬ führungsbeispielen nach Fig. 1 und Fig. 2 der Haupt¬ bremszylinderdruck wirkt.The fact that the accumulator pressure chamber 319 is arranged on the membrane 324, on which the master brake cylinder pressure acts in the exemplary embodiments according to FIGS. 1 and 2, mainly contributes to the shortening of the overall length.
Der Ventilstößel 323 geht zur Membran 324 hin in einen Kolben 332 über, welcher abgedichtet in die Speicher¬ druckkammer 319 geführt ist. Der Kolben 332 besitzt eine starre Verbindung zur Membran 324. Während der Druck im Niederdruckspeicher also als Wirkfläche in Schließrichtung des Umschaltventils die Differenzfläche aus der Membranfläche und dem Quer¬ schnitt des Kolbens 332 besitzt, wirkt der Druck im Hauptbremsyzylinder bei geöffnetem Ventil nur noch auf die Querschnittsfläche des Kolbens 332. Da diese Querschnittsfläche des Kolbens 232 jedoch kleiner ist als die vom Schließglied 321 abgedeckte Fläche am Ventilsitz 321, vermag die Pumpe wie im Beispiel zuvor das Ventil nicht zu öffnen, wenn der Niederdruck¬ speicher gefüllt ist, die Speicherdruckkammer 319 also unter Druck steht. Dies ist aus den zuvor beschriebenen Gründen auch nicht nötig. The valve tappet 323 merges with the diaphragm 324 into a piston 332, which is sealingly guided into the accumulator pressure chamber 319. The piston 332 has a rigid connection to the membrane 324. While the pressure in the low-pressure accumulator is the effective area in the closing direction of the changeover valve Differential area from the membrane area and the cross section of the piston 332, the pressure in the master brake cylinder only acts on the cross-sectional area of the piston 332 when the valve is open. However, since this cross-sectional area of the piston 232 is smaller than the area on the valve seat 321 covered by the closing member 321 , as in the example above, the pump is unable to open the valve when the low-pressure accumulator is full, ie the accumulator pressure chamber 319 is under pressure. This is not necessary for the reasons described above.
BezugszeichenlisteReference list
1 Hauptbremszylinder1 master brake cylinder
2 Nachlaufbehälter2 trailing containers
3 Bremsleitung3 brake line
4 Einlaßventil4 inlet valve
5 Auslaßventil5 exhaust valve
6 Radbremszy1Inder6 wheel brake cylinders
7 erste Saugleitung7 first suction line
8 zweite Saugleitung8 second suction line
9 Niederdruckspeicher9 low pressure accumulators
10 Pumpe10 pump
11 Druckleitung11 pressure line
12 Rücklaufleitung12 return line
13 Trennven i113 separation veins i1
14 Umschaltventil14 changeover valve
15 Steuerleitung15 control line
16 Auslaßkammer16 outlet chamber
17 Einlaßkammer17 inlet chamber
18 Federkammer18 spring chamber
19 Speicherdruckkammer19 accumulator pressure chamber
20 Ausgleichskammer20 compensation chamber
21 Schließglied21 closing member
22 Ventilsitz22 valve seat
23 Ventilstößel23 valve lifters
24 Membran24 membrane
25 Druckfeder25 compression spring
26 Druckfeder26 compression spring
27 Stufenkolben Druckfeder27 step piston Compression spring
UmschaltventilDiverter valve
EinlaßkammerInlet chamber
SpeicherdruckkammerAccumulator pressure chamber
AusgleichskammerCompensation chamber
SchließgliedClosing link
VentilsitzValve seat
Druckfedercompression spring
StufenkolbenStepped piston
Druckfedercompression spring
Bohrungdrilling
Druckfedercompression spring
Stiftpen
UmschaltventilDiverter valve
SpeicherdruckkammmerAccumulator chamber
SchließgliedClosing link
VentilsitzValve seat
StufenkolbenStepped piston
Stiftpen
UmschaltventilDiverter valve
SpeicherdruckkammerAccumulator pressure chamber
SchließgliedClosing link
VentilsitzValve seat
VentilstößelValve lifter
Membranmembrane
Kolben piston

Claims

Patentansprüche Claims
1. Bremsanlage mit einer Einrichtung zum Regeln sowohl des Bremsschlupfes als auch des Antriebsschlupfes, mit einem Hauptbremszylinder (1) der an einen Nachlaufbehälter (2) angeschlossen ist, mit mindestens einem Radbremszylinder (6), der über eine Bremsleitung (3) mit dem Hauptbremszylinder (1) verbunden ist und zu einem angetriebenen Rad gehört, mit einr selbstansaugenden Pumpe (10), welche mit ihrer Saugseite über eine erste Saugleitung (7) mit einem Niederdruckspeicher (9) und über eine zweite Saugleitung (8) mit der Bremsleitung verbunden ist und welche mit ihrer Druckseite über eine Durckleitung (11) an die Bremleitung (3) zwischen der Einmündung der zweiten Saugleitung (8) und dem Radbremszylinder (6) anschließt, mit einem Einlaßventil(4) in der Bremsleitung (3) zwischen dem Einmündungspunkt der Druckleitung (11) und dem Radbremzylinder (6), mit einem Auslaßventil (5) in einer Rücklaufleitung (12) zwischen dem Radbremszylinder (6) und dem Niederdruckspeicher (9) mit einem Trennventil (19) in der Bremsleitung (3) zwischen den Einmündungspunkten der zweiten Saugleitung (8) und der Druckleitung (11) und mit einem in Grundstellung offenen, hydraulisch betätigten Umschaltventil (14,114,214,314) mit Schließglied (21,121,221,321) und Ventilsitz (22,122,222,322) in der zweiten Saugleitung (8) , dadurch g e k e n n z e i c h n e t, daß der Druck im Niederdruckspeicher (9) eine Wirkfläche in Schließrichtung des Umschaltventils (14,114,214,314) besitzt.1. Brake system with a device for regulating both the brake slip and the drive slip, with a master brake cylinder (1) which is connected to a caster tank (2), with at least one wheel brake cylinder (6) connected to the master brake cylinder via a brake line (3) (1) and belongs to a driven wheel, with a self-priming pump (10), which is connected with its suction side via a first suction line (7) to a low-pressure accumulator (9) and via a second suction line (8) to the brake line and which connects with its pressure side via a pressure line (11) to the brake line (3) between the mouth of the second suction line (8) and the wheel brake cylinder (6), with an inlet valve (4) in the brake line (3) between the point of confluence Pressure line (11) and the wheel brake cylinder (6), with an outlet valve (5) in a return line (12) between the wheel brake cylinder (6) and the low pressure accumulator (9) with a separating valve (19) in the brake line (3) between the junction points of the second suction line (8) and the pressure line (11) and with a hydraulically operated changeover valve (14,114,214,314) with a closing element (21,121,221,321) and valve seat (22,122,222,322) open in the basic position in the second suction line (8), characterized in that the pressure in the low-pressure accumulator (9) has an effective area in the closing direction of the changeover valve (14, 114, 214, 314).
2. Bremsanlage nach Anspruch 1, dadurch g e k e n n z e i c h n e t, daß zumindest bei geschlossenem Umschaltventil (14,114,214,314) der Druck des HauptbremsZylinders (1) in Schließrichtung des Umschaltventils (14,114,214,314) wirkt.2. Brake system according to claim 1, characterized in that the pressure of the master brake cylinder (1) acts in the closing direction of the changeover valve (14,114,214,314) at least when the changeover valve (14,114,214,314) is closed.
3. Bremsanlage nach Anspruch 1 oder 2, dadurch g e k e n n z e i c h n e t, daß das Umschaltventil (14,114,214,314) abhängig vom Hub eines mit dem Niederdruckspeicherdruck (Speicherdruckkammer 19,119,219) beaufschlagten Kolbens (27,127,227) gesteuert wird.3. Braking system according to claim 1 or 2, characterized in that the changeover valve (14, 114, 214, 314) is controlled depending on the stroke of a piston (27, 127, 227) acted upon by the low-pressure accumulator pressure (accumulator pressure chamber 19, 119, 219).
4. Bremsanlage nach Anspruch 3, dadurch g e k e n n z e i c h n e t, daß der Kolben (127,227) den Niederdruckspeicher (Speicherdruckkammer 119,219) begrenzt. 4. Brake system according to claim 3, characterized in that the piston (127, 227) limits the low-pressure accumulator (accumulator pressure chamber 119, 219).
5. Bremsanlage nach Anspruch 3, dadurch g e k e n n z e i c h n e t, daß der Kolben (27,127,227) von der Druckfeder (28,128) in Öf nungsrichtung des Umschaltventils (14,114,214) beaufschlagt ist.5. Brake system according to claim 3, characterized in that the piston (27, 127, 227) is acted upon by the compression spring (28, 128) in the opening direction of the changeover valve (14, 114, 214).
6. Bremsanlage nach einem der Ansprüche 3 bis 5, dadurch g e k e n n z e i c h n e t, daß zwischen dem Kolben (127,227) und dem Schließglied (121,221) eine gefesselte Druckfeder (130) angeordnet ist.6. Brake system according to one of claims 3 to 5, characterized in that a tethered compression spring (130) is arranged between the piston (127, 227) and the closing member (121, 221).
7. Bremsanlage nach einem der Ansprüche 3 bis 6, dadurch g e k e n n z e i c h n e t, daß zwischen dem Kolben (227) und dem Schließglied (221) eine Mitnehmerverbindung besteht, welche bei Entleerung des Niederdruckspeichers (Speicherdruckkammer 219) das Schließglied (221) vom Ventilsitz (222) abhebt.7. Brake system according to one of claims 3 to 6, characterized in that there is a driver connection between the piston (227) and the closing member (221) which, when the low-pressure accumulator (storage pressure chamber 219) is emptied, the closing member (221) from the valve seat (222) takes off.
8. Bremsanlage nach einem der Ansprüche 1 oder 2, dadurch g e k e n n z e i c h n e t, daß das Umschaltventil (314) abhängig vom Hub einer mit dem Niederdruckspeicherdruck beaufschlagten Membran (324) gesteuert wird.8. Brake system according to one of claims 1 or 2, characterized in that the changeover valve (314) is controlled as a function of the stroke of a diaphragm (324) acted upon by the low-pressure accumulator pressure.
9. Bremsanlage nach Anspruch 8, dadurch g e k e n n z e i c h n e t, daß zwischen Membran (324) und Schließglied (321) eine starre Verbindung besteht. 9. Brake system according to claim 8, characterized in that there is a rigid connection between the diaphragm (324) and the closing member (321).
PCT/EP1994/001517 1993-06-09 1994-05-11 Slip-controlled hydraulic brake system WO1994029149A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4319161.4 1993-06-09
DE19934319161 DE4319161A1 (en) 1993-06-09 1993-06-09 Slip-controlled hydraulic brake system

Publications (1)

Publication Number Publication Date
WO1994029149A1 true WO1994029149A1 (en) 1994-12-22

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WO (1) WO1994029149A1 (en)

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