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WO1994029149A1 - Systeme de freinage hydraulique a regulation antipatinage - Google Patents

Systeme de freinage hydraulique a regulation antipatinage 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)
English (en)
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/fr

Links

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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Regulating Braking Force (AREA)

Abstract

L'invention concerne un système de freinage antiblocage, antipatinage qui fonctionne, en mode antiblocage, selon le principe de la recirculation et qui est pourvu d'une pompe à auto-amorçage. Afin d'assurer la régulation antipatinage, la pompe prélève du fluide hydraulique dans le réservoir d'alimentation (2), en passant par le maître-cylindre (1). Une soupape d'inversion (14) est montée dans la conduite d'aspiration (8) située entre le côté aspiration de la pompe (10) et le maître-cylindre (1). Afin que la soupape d'inversion (14) n'ait pas à se fermer à chaque freinage déclenché par pression, aussi légère soit-elle, de la pédale de frein, ladite soupape est commutable en fonction de la pression régnant dans le réservoir basse pression (9). La soupape d'inversion (14) est de ce fait toujours fermée lorsque le réservoir basse pression (9) est rempli. La soupape peut également être actionnée par la pression régnant dans le maître-cylindre. L'inversion ne peut alors s'opérer qu'avec des pressions de freinage supérieures à 5 bar.
PCT/EP1994/001517 1993-06-09 1994-05-11 Systeme de freinage hydraulique a regulation antipatinage WO1994029149A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4319161.4 1993-06-09
DE19934319161 DE4319161A1 (de) 1993-06-09 1993-06-09 Schlupfgeregelte hydraulische Bremsanlage

Publications (1)

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

Family

ID=6489992

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1994/001517 WO1994029149A1 (fr) 1993-06-09 1994-05-11 Systeme de freinage hydraulique a regulation antipatinage

Country Status (2)

Country Link
DE (1) DE4319161A1 (fr)
WO (1) WO1994029149A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998040257A1 (fr) * 1997-03-13 1998-09-17 Robert Bosch Gmbh Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19508331A1 (de) * 1995-03-09 1996-09-12 Teves Gmbh Alfred Bremsanlage
DE19514171A1 (de) * 1995-04-15 1996-10-17 Teves Gmbh Alfred Hydraulische Bremsanlage mit elektronischer Bremsdruckregelung
DE19534456A1 (de) * 1995-09-16 1997-03-20 Teves Gmbh Alfred Hydraulische Bremsanlage mit Vordruckerzeuger
DE19626289B4 (de) * 1996-07-01 2008-08-14 Continental Teves Ag & Co. Ohg Hydraulische Bremsanlage mit einer Rückförderpumpe

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2119883A (en) * 1982-04-28 1983-11-23 Bosch Gmbh Robert Anti-skid anti-spin regulation for vehicle wheels
WO1992005990A1 (fr) * 1990-10-05 1992-04-16 Alfred Teves Gmbh Systeme de freinage avec installation servant a la fois pour la regulation du glissement au freinage et pour la regulation du glissement a l'entrainement
DE4205041A1 (de) * 1991-02-20 1992-08-27 Tokico Ltd Kraftfahrzeugbremsvorrichtung
EP0526276A1 (fr) * 1991-07-30 1993-02-03 Alliedsignal Europe Services Techniques Dispositif de régulation de pression pour circuit hydraulique
EP0539899A1 (fr) * 1991-10-30 1993-05-05 Sumitomo Electric Industries, Limited Dispositif de contrôle de pression de fluide de freinage

Family Cites Families (12)

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Publication number Priority date Publication date Assignee Title
JPH048655A (ja) * 1990-04-25 1992-01-13 Sumitomo Electric Ind Ltd アンチロック装置を備えたブレーキ回路
DE4016752A1 (de) * 1990-05-25 1991-11-28 Teves Gmbh Alfred Bremsdruckregelvorrichtung und verfahren zu ihrer anwendung
DE4028552A1 (de) * 1990-09-08 1992-03-12 Teves Gmbh Alfred Hydraulische bremsanlage fuer ein kraftfahrzeug mit angetriebenen und nichtangetriebenen raedern
DE4038033A1 (de) * 1990-11-29 1992-06-04 Teves Gmbh Alfred Blockiergeschuetzte, hydraulische bremsanlage
DE4108640A1 (de) * 1991-03-16 1992-09-17 Teves Gmbh Alfred Blockiergeschuetzte, hydraulische bremsanlage
DE4118951A1 (de) * 1991-06-08 1992-12-10 Teves Gmbh Alfred Hydraulische bremsanlage mit blockierschutzregelung
DE4121604A1 (de) * 1991-06-29 1993-01-07 Bosch Gmbh Robert Hydraulische bremsanlage mit blockierschutz- und antriebsschlupfregeleinrichtung, insbesondere fuer kraftfahrzeuge
JPH05246312A (ja) * 1992-03-05 1993-09-24 Tokico Ltd ブレーキ液圧制御装置
DE4128091C2 (de) * 1991-08-24 1998-02-26 Teves Gmbh Alfred Bremsanlage mit Blockierschutz- und Antriebsschlupfregelung
DE4136109C2 (de) * 1991-11-02 2001-10-18 Continental Teves Ag & Co Ohg Schlupfgeregelte hydraulische Bremsanlage
DE4202388A1 (de) * 1992-01-29 1993-08-05 Bosch Gmbh Robert Hydraulische bremsanlage mit blockierschutz- und antriebsschlupf-regeleinrichtung, insbesondere fuer kraftfahrzeuge
DE4213205A1 (de) * 1992-04-22 1993-10-28 Teves Gmbh Alfred Bremsdruckregelvorrichtung für eine hydraulische Kraftfahrzeugbremsanlage

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2119883A (en) * 1982-04-28 1983-11-23 Bosch Gmbh Robert Anti-skid anti-spin regulation for vehicle wheels
WO1992005990A1 (fr) * 1990-10-05 1992-04-16 Alfred Teves Gmbh Systeme de freinage avec installation servant a la fois pour la regulation du glissement au freinage et pour la regulation du glissement a l'entrainement
DE4108756A1 (de) * 1990-10-05 1992-09-24 Teves Gmbh Alfred Kraftfahrzeugbremsanlage mit schlupfabhaengiger regelung des bremsdruckes
DE4205041A1 (de) * 1991-02-20 1992-08-27 Tokico Ltd Kraftfahrzeugbremsvorrichtung
EP0526276A1 (fr) * 1991-07-30 1993-02-03 Alliedsignal Europe Services Techniques Dispositif de régulation de pression pour circuit hydraulique
EP0539899A1 (fr) * 1991-10-30 1993-05-05 Sumitomo Electric Industries, Limited Dispositif de contrôle de pression de fluide de freinage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
BOSCH TECHNISCHE BERICHTE Band 7 (1980) Heft 2 ISSN 0006-789 X Antiblockiersystem (ABS) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998040257A1 (fr) * 1997-03-13 1998-09-17 Robert Bosch Gmbh Soupape d'arret a commande hydraulique et systeme de freinage hydraulique de vehicule

Also Published As

Publication number Publication date
DE4319161A1 (de) 1994-12-15

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