EP1251282B1 - Vehicle braking system with a gas hydraulic accumulator - Google Patents

Vehicle braking system with a gas hydraulic accumulator Download PDF

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Publication number
EP1251282B1
EP1251282B1 EP02016285A EP02016285A EP1251282B1 EP 1251282 B1 EP1251282 B1 EP 1251282B1 EP 02016285 A EP02016285 A EP 02016285A EP 02016285 A EP02016285 A EP 02016285A EP 1251282 B1 EP1251282 B1 EP 1251282B1
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EP
European Patent Office
Prior art keywords
piston
pressure accumulator
gas
gas pressure
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02016285A
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German (de)
French (fr)
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EP1251282A3 (en
EP1251282A2 (en
Inventor
Kurt Mohr
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Lucas Varity GmbH
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Lucas Varity GmbH
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Filing date
Publication date
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Publication of EP1251282A2 publication Critical patent/EP1251282A2/en
Publication of EP1251282A3 publication Critical patent/EP1251282A3/en
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Publication of EP1251282B1 publication Critical patent/EP1251282B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/22—Liquid port constructions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/04—Accumulators
    • F15B1/08—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor
    • F15B1/10—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means
    • F15B1/103—Accumulators using a gas cushion; Gas charging devices; Indicators or floats therefor with flexible separating means the separating means being bellows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/20—Accumulator cushioning means
    • F15B2201/205—Accumulator cushioning means using gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/31—Accumulator separating means having rigid separating means, e.g. pistons
    • F15B2201/312—Sealings therefor, e.g. piston rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/315—Accumulator separating means having flexible separating means
    • F15B2201/3153—Accumulator separating means having flexible separating means the flexible separating means being bellows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/315—Accumulator separating means having flexible separating means
    • F15B2201/3158—Guides for the flexible separating means, e.g. for a collapsed bladder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/30—Accumulator separating means
    • F15B2201/32—Accumulator separating means having multiple separating means, e.g. with an auxiliary piston sliding within a main piston, multiple membranes or combinations thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/41—Liquid ports
    • F15B2201/411—Liquid ports having valve means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2201/00—Accumulators
    • F15B2201/40—Constructional details of accumulators not otherwise provided for
    • F15B2201/415—Gas ports
    • F15B2201/4155—Gas ports having valve means

Definitions

  • the invention relates to a gas pressure accumulator for a vehicle brake system, the one Housing, whose interior by a metal bellows and on the metal bellows gas-tight mounted disc in a gas-filled gas space and a Fluid space is divided, wherein the fluid space through a supply line, a fluid under pressure can be supplied and removed, and between the fluid space and the supply line Valve arrangement is provided which closes when the pressure in the supply line Minimum value, and opens when the pressure exceeds the minimum value, wherein the metal bellows performs a lifting movement during the supply and removal of the fluid, by means of which the valve arrangement is actuated. Furthermore, the invention relates to a equipped with such a gas pressure accumulator vehicle brake system.
  • the fluid space such gas pressure accumulator is in operation of the vehicle brake system partially or completely filled with brake fluid against the pressure in the gas space to this save.
  • DE 1 232 418 describes a hydro-pneumatic pressure accumulator, which is a cylindrical Housing and projecting into the housing central guide tube comprises.
  • outlet openings allow the Zu- or Discharge of fluid into and out of a fluid space from one of the guide tube surrounding elastic partition as well as a sealing with the elastic Dividing wall connected closing body is limited.
  • the closing body slides under deformation of the Partition with low friction on the guide tube.
  • US 3,939,872 discloses a pressure accumulator comprising a housing, one in the housing arranged metal bellows and connected to the metal bellows cone includes. With a supply of fluid in a formed in the housing and through the cone-bounded chamber is due to the cone connected to a rod shifted the fluid pressure, whereby the metal bellows is compressed. The with the Cone-linked rod is in a from an upper wall of the housing led extending projection.
  • the object of the invention is therefore to provide a compact, safe and reliable Gas pressure accumulator for a vehicle brake system and one with such Gas pressure accumulator equipped vehicle brake system provide.
  • the object is achieved by a gas pressure accumulator of the aforementioned Art solved, having the features of claim 1. Further, the task is by a vehicle brake system equipped with such a gas pressure accumulator solved. Since the metal bellows when supplying and discharging the fluid a lifting movement performs, by means of which the valve assembly is actuated is the completion of the Fluid space directly coupled with the movement of the metal bellows, creating a in Closed safety system is formed.
  • a piston is preferably performed in the hollow cylinder.
  • the hollow cylinder to be guided on a piston. This is a guided movement the piston and the sealing seats formed on the hollow cylinder relative to each other possible and at the same time is a compact design of the gas pressure accumulator achieved.
  • An advantageous embodiment provides that the lifting movement of the metal bellows of Two end stops is limited to defined end positions for the moving components pretend. In the end positions, the valve assembly is at the same time each closed.
  • At least one end stop is advantageous a seal or a sealing seat educated.
  • a redundant seal is formed on the end stop, which allows a particularly good seal.
  • the redundant sealing becomes special Advantageously arranged on the end stop, which is the basic position of the piston limited.
  • the gas pressure accumulator is particularly well sealed when the pressure in the supply line is less than the permissible minimum pressure.
  • the pressure in the Supply line the so-called system pressure of the vehicle brake system, in particular for longer vehicle downtime below this minimum pressure, the so-called Gas pressure, sink.
  • the gas pressure accumulator may also be provided with a valve arrangement which with but at least one redundant seal is provided at an end stop does not have the dual function described above.
  • the piston touches as a closing element in a closing movement first a first sealing seat and seals at this.
  • the piston touches a second sealing seat, which forms an end stop for the closing element, and seals redundantly at this.
  • the first sealing seat may be one of those described above Corresponding sealing surfaces.
  • the piston advantageously arranged at least one seal against at least one Sealing seat can seal.
  • gas pressure accumulator 10 has a cup-shaped Housing 12, which is closed by a cover 14.
  • the interior of the Housing 12 is of a subsequent to the lid 14 metal bellows 16 and a gas-tight attached disc 18 in a gas space 20 and a fluid space 22nd divided.
  • the gas space 20 is filled with a pressurized gas.
  • the lid 14 is pierced by a supply line 24, through which the fluid space 22 a fluid is supplied when the pressure in the supply line 24 increases. The fluid is in the fluid space 22 stored and discharged from this when the pressure in the supply line 24 drops.
  • the housing 12 has a cylindrical outer wall 26 with a longitudinal axis 28.
  • To the outer wall 26 includes a disc-shaped end wall 30, in the coaxial a threaded bore 32 is formed, through which in the gas space 20, the gas with can be supplied to a so-called gas supply pressure.
  • the threaded bore 32 is closed with a screw plug 34 which rests on a sealing washer 36.
  • the lid 14 has a disc-shaped closure portion 38 which by means of a circumferentially formed paragraph 40 in the outer wall 26 of the housing 12 centered and supported on this.
  • the disc-shaped closure portion 38 is connected to the outer wall 26 by a weld 42 gas-tight.
  • Fig. 1 are at the interior of the Housing 12 facing side of the closure portion 38 coaxial with a hollow cylinder 44 and a mandrel 46 integrally formed.
  • a terminal 48 integrally formed by the in essential axially directed bores 50, 52 and 54 with the interior of the Housing 12 is connected.
  • the metal bellows 16 is folded, substantially cylindrical and at its two axial ends through welds 56 and 58 with the closure portion 38 and the disc 18 connected gas-tight.
  • the disc 18 is directed normal to the axis and with a coaxial rod 60 in one piece connected, in which an axial bore 62 is formed, by means of which the rod 60th is guided on the mandrel 46.
  • a piston 64 To the rod 60 integrally connects a piston 64, whose diameter is larger than that of the rod 60.
  • sealing surfaces 66 and 68 are formed, which are axially directed and each form a sealing seat.
  • Axial between the sealing surfaces 66 and 68 is a recess 70 formed on the inner circumference of the hollow cylinder 44, so that its Diameter in this area greater than the diameter of the sealing seats on the Sealing surfaces 66 and 68 is.
  • the piston 64 has a circumferential groove in which a seal 72 in the form of a Sealing ring is inserted or injected.
  • the gasket 72 is formed to be cooperates with the sealing surface 66 or 68 and thereby a valve assembly 74th forms, which can seal two times liquid-tight.
  • Fig. 1 the metal bellows 16 is shown in a position in which almost no fluid is stored in the gas pressure accumulator 10, so the pressure in the fluid space 22 its Minimum value, the gas form has reached.
  • the piston 64 is here almost in a normal position, in which the seal 72 bears against the sealing surface 66 and seals at this.
  • the hollow cylinder 44th and the closure portion 38 of the lid 14 created a so-called vestibule 76, the only connected through the bore 52 to the terminal 48, otherwise but is complete.
  • the valve assembly is thus between the supply line 24 and the fluid space 22 is closed. As from the fluid space 22 no fluid in the vestibule 76 can remain, even with a drop in pressure at port 48 of Pressure in the fluid space 22 constant and limited to the minimum value.
  • the metal bellows 16 is thus safe against damage due to pressure drop protected.
  • the piston 64 with the seal 72 each slide along an axial stroke X 1 and X 2 .
  • the seal remains, while a low pressure equalization between the fluid chamber 22 and the vestibule 76 is possible. In this way, elasticity and thermal expansion can be compensated as described above.
  • a Seal 82 is used, which, together with one on the piston 64 opposite trained sealing seat 84 a redundant sealing of the piston 64 in the Basic position forms.
  • the seal 82 may alternatively be inserted in the piston 64.
  • an end stop 86 is formed inside, against which the Disc 18 in relation to FIG. 1 upper end position of the piston 64 abuts.
  • Fig. 2 shows an embodiment of a gas pressure accumulator 10, which is similar to is shown in Fig. 1 is constructed.
  • this gas pressure accumulator 10 is the Disc 18 integrally connected to the rod 60 and a hollow cylinder 44 '.
  • the Rod 60 is axially slidably guided in a bore 54 'of the mandrel 46 and of a hole 62 'passes, which connects the bore 50 with the vestibule 76.
  • a piston 64' integrally formed at the hollow cylinder 44 'facing the end of the mandrel 46.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Braking Systems And Boosters (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

The system has a gas hydraulic accumulator (10) with a casing (12), which is divided by metal bellows (16) into gas (20) and fluid (22) chambers. A valve assembly (74) between the fluid chamber and a supply line (24) for the fluid chamber closes if the pressure in the supply line falls below a minimum value or exceeds a maximum value and opens if the pressure exceeds the minimum value and falls below the maximum value. An Independent claim is included for a gas hydraulic accumulator for use in the system.

Description

Hintergrund der ErfindungBackground of the invention

Die Erfindung betrifft einen Gasdruckspeicher für eine Fahrzeugbremsanlage, der ein Gehäuse aufweist, dessen Innenraum durch einen Metallbalg und eine an dem Metallbalg gasdicht befestigte Scheibe in einen mit Gas gefüllten Gasraum und einen Fluidraum geteilt ist, wobei dem Fluidraum durch eine Zuleitung ein Fluid unter Druck zu- und abgeführt werden kann, und zwischen dem Fluidraum und der Zuleitung eine Ventilanordnung vorgesehen ist, die schließt, wenn der Druck in der Zuleitung einen Minimalwert unterschreitet, und öffnet, wenn der Druck den Minimalwert überschreitet, wobei der Metallbalg beim Zu- und Abführen des Fluids eine Hubbewegung ausführt, mittels der die Ventilanordnung betätigt wird. Ferner betrifft die Erfindung eine mit einem derartigen Gasdruckspeicher ausgestattete Fahrzeugbremsanlage.The invention relates to a gas pressure accumulator for a vehicle brake system, the one Housing, whose interior by a metal bellows and on the metal bellows gas-tight mounted disc in a gas-filled gas space and a Fluid space is divided, wherein the fluid space through a supply line, a fluid under pressure can be supplied and removed, and between the fluid space and the supply line Valve arrangement is provided which closes when the pressure in the supply line Minimum value, and opens when the pressure exceeds the minimum value, wherein the metal bellows performs a lifting movement during the supply and removal of the fluid, by means of which the valve arrangement is actuated. Furthermore, the invention relates to a equipped with such a gas pressure accumulator vehicle brake system.

Der Fluidraum derartiger Gasdruckspeicher wird im Betrieb der Fahrzeugbremsanlage gegen den Druck im Gasraum teilweise oder ganz mit Bremsfluid gefüllt, um dieses zu speichern.The fluid space such gas pressure accumulator is in operation of the vehicle brake system partially or completely filled with brake fluid against the pressure in the gas space to this save.

Die DE 1 232 418 beschreibt einen hydro-pneumatischen Druckspeicher, der ein zylindrisches Gehäuse sowie ein in das Gehäuse ragendes zentrales Führungsrohr umfaßt. In dem Führungsrohr ausgebildete Austrittsöffnungen ermöglichen die Zu- bzw. Abfuhr von Fluid in einen bzw. aus einem Fluidraum, der von einer das Führungsrohr umgebenden elastischen Trennwand sowie einem abdichtend mit der elastischen Trennwand verbundenen Schließkörper begrenzt wird. Zum Öffnen bzw. Schließen der Austrittsöffnungen gleitet der Schließkörper unter Verformung der Trennwand reibungsarm auf dem Führungsrohr.DE 1 232 418 describes a hydro-pneumatic pressure accumulator, which is a cylindrical Housing and projecting into the housing central guide tube comprises. In the guide tube formed outlet openings allow the Zu- or Discharge of fluid into and out of a fluid space from one of the guide tube surrounding elastic partition as well as a sealing with the elastic Dividing wall connected closing body is limited. To open or Closing the outlet openings, the closing body slides under deformation of the Partition with low friction on the guide tube.

Die US 3,939,872 offenbart einen Druckspeicher, der ein Gehäuse, einen in dem Gehäuse angeordneten Metallbalg sowie einen mit dem Metallbalg verbundenen Kegel umfaßt. Bei einer Zufuhr von Fluid in eine in dem Gehäuse ausgebildete und durch den Kegel begrenzte Kammer wird der mit einer Stange verbundene Kegel infolge des Fluiddruckes verschoben, wodurch der Metallbalg komprimiert wird. Die mit dem Kegel verbundene Stange ist in einem sich von einer oberen Wand des Gehäuses erstreckenden Vorsprung geführt.US 3,939,872 discloses a pressure accumulator comprising a housing, one in the housing arranged metal bellows and connected to the metal bellows cone includes. With a supply of fluid in a formed in the housing and through the cone-bounded chamber is due to the cone connected to a rod shifted the fluid pressure, whereby the metal bellows is compressed. The with the Cone-linked rod is in a from an upper wall of the housing led extending projection.

Der Erfindung zugrundeliegendes ProblemThe problem underlying the invention

Bei Fahrzeugbremsanlagen bestehen bezüglich der Funktionsfähigkeit und Sicherheit der Aggregate besonders hohe Anforderungen.In vehicle brake systems exist in terms of functionality and safety the aggregates particularly high requirements.

Aufgabe der Erfindung ist es daher, einen kompakten, sicheren und zuverlässigen Gasdruckspeicher für eine Fahrzeugbremsanlage sowie eine mit einem derartigen Gasdruckspeicher ausgestattete Fahrzeugbremsanlage bereitzustellen.The object of the invention is therefore to provide a compact, safe and reliable Gas pressure accumulator for a vehicle brake system and one with such Gas pressure accumulator equipped vehicle brake system provide.

Erfindungsgemäße LösungInventive solution

Die Aufgabe ist erfindungsgemäß durch einen Gasdruckspeicher der eingangs genannten Art gelöst, der die Merkmale des Anspruchs 1 aufweist. Ferner ist die Aufgabe durch eine mit einem derartigen Gasdruckspeicher ausgestattete Fahrzeugbremsanlage gelöst. Da der Metallbalg beim Zu- und Abführen des Fluids eine Hubbewegung ausführt, mittels der die Ventilanordnung betätigt wird ist das Abschließen des Fluidraums unmittelbar mit der Bewegung des Metallbalgs gekoppelt, wodurch ein in sich geschlossenes Sicherheitssystem gebildet ist. The object is achieved by a gas pressure accumulator of the aforementioned Art solved, having the features of claim 1. Further, the task is by a vehicle brake system equipped with such a gas pressure accumulator solved. Since the metal bellows when supplying and discharging the fluid a lifting movement performs, by means of which the valve assembly is actuated is the completion of the Fluid space directly coupled with the movement of the metal bellows, creating a in Closed safety system is formed.

Vorteilhafte AusgestaltungenAdvantageous embodiments

Weiterbildungen der Erfindung sind Gegenstand der abhängigen Ansprüche.Further developments of the invention are the subject of the dependent claims.

In dem Hohlzylinder ist vorzugsweise ein Kolben geführt. Alternativ dazu kann auch der Hohlzylinder auf einem Kolben geführt sein. Dadurch ist eine geführte Bewegung des Kolbens und der an dem Hohlzylinder ausgebildeten Dichtsitze relativ zueinander möglich und zugleich wird eine kompakte Bauform des Gasdruckspeichers erzielt.In the hollow cylinder, a piston is preferably performed. Alternatively, too the hollow cylinder to be guided on a piston. This is a guided movement the piston and the sealing seats formed on the hollow cylinder relative to each other possible and at the same time is a compact design of the gas pressure accumulator achieved.

Eine vorteilhafte Ausgestaltung sieht vor, daß die Hubbewegung des Metallbalgs von zwei Endanschlägen begrenzt ist, um definierte Endlagen für die beweglichen Bauteile vorzugeben. In den Endlagen ist die Ventilanordnung zugleich jeweils geschlossen.An advantageous embodiment provides that the lifting movement of the metal bellows of Two end stops is limited to defined end positions for the moving components pretend. In the end positions, the valve assembly is at the same time each closed.

An mindestens einem Endanschlag ist vorteilhaft eine Dichtung oder ein Dichtsitz ausgebildet. Dadurch ist am Endanschlag eine redundante Abdichtung ausgebildet, die eine besonders gute Abdichtung ermöglicht. Die redundante Abdichtung wird besonders vorteilhaft an dem Endanschlag angeordnet, der die Grundstellung des Kolbens begrenzt. Dadurch ist der Gasdruckspeicher besonders gut abgedichtet, wenn der Druck in der Zuleitung kleiner als der zulässige Minimaldruck ist. Der Druck in der Zuleitung, der sogenannte Systemdruck der Fahrzeugbremsanlage, kann insbesondere bei längeren Fahrzeugstillstandszeiten unter diesen Minimaldruck, den sogenannten Gasvordruck, sinken.At least one end stop is advantageous a seal or a sealing seat educated. As a result, a redundant seal is formed on the end stop, which allows a particularly good seal. The redundant sealing becomes special Advantageously arranged on the end stop, which is the basic position of the piston limited. As a result, the gas pressure accumulator is particularly well sealed when the pressure in the supply line is less than the permissible minimum pressure. The pressure in the Supply line, the so-called system pressure of the vehicle brake system, in particular for longer vehicle downtime below this minimum pressure, the so-called Gas pressure, sink.

Der Gasdruckspeicher kann auch mit einer Ventilanordnung versehen sein, die mit mindestens einer redundanten Abdichtung an einem Endanschlag versehen ist, aber nicht die oben beschriebene Doppelfunktion aufweist. Bei einer solchen Ventilanordnung berührt der Kolben als Schließelement bei einer Schließbewegung zuerst einen ersten Dichtsitz und dichtet an diesem ab. Anschließend berührt der Kolben einen zweiten Dichtsitz, der einen Endanschlag für das Schließelement bildet, und dichtet redundant an diesem ab. Der erste Dichtsitz kann einer der oben beschriebenen Dichtflächen entsprechen. The gas pressure accumulator may also be provided with a valve arrangement which with but at least one redundant seal is provided at an end stop does not have the dual function described above. In such a valve arrangement the piston touches as a closing element in a closing movement first a first sealing seat and seals at this. Then the piston touches a second sealing seat, which forms an end stop for the closing element, and seals redundantly at this. The first sealing seat may be one of those described above Corresponding sealing surfaces.

Um die erforderliche Dichtheit der Ventilanordnung zu gewährleisten, ist am Kolben vorteilhaft mindestens eine Dichtung angeordnet, die gegen mindestens einen Dichtsitz abdichten kann.To ensure the required tightness of the valve assembly is on the piston advantageously arranged at least one seal against at least one Sealing seat can seal.

Kurzbeschreibung der ZeichnungenBrief description of the drawings

Weitere Merkmale und Eigenschaften werden anhand der Beschreibung zweier Ausführungsformen unter Bezugnahme auf die beigefügten Zeichnungen erläutert.

Fig. 1
zeigt eine erste Ausführungsform eines erfindungsgemäßen Gasdruckspeichers im Längsschnitt.
Fig. 2
zeigt eine zweite Ausführungsform eines erfindungsgemäßen Gasdruckspeichers im Längsschnitt.
Further features and properties will be explained with reference to the description of two embodiments with reference to the accompanying drawings.
Fig. 1
shows a first embodiment of a gas pressure accumulator according to the invention in longitudinal section.
Fig. 2
shows a second embodiment of a gas pressure accumulator according to the invention in longitudinal section.

Detaillierte Beschreibung derzeit bevorzugter AusführungsformenDetailed Description of Presently Preferred Embodiments

Ein in den Fig. 1 und 2 dargestellter Gasdruckspeicher 10 weist ein becherförmiges Gehäuse 12 auf, das mit einem Deckel 14 verschlossen ist. Der Innenraum des Gehäuses 12 ist von einem an den Deckel 14 anschließenden Metallbalg 16 und einer daran gasdicht befestigten Scheibe 18 in einen Gasraum 20 und einen Fluidraum 22 geteilt. Der Gasraum 20 ist mit einem unter Druck stehenden Gas gefüllt. Der Deckel 14 ist von einer Zuleitung 24 durchbrochen, durch die dem Fluidraum 22 ein Fluid zugeführt wird, wenn der Druck in der Zuleitung 24 steigt. Das Fluid wird im Fluidraum 22 gespeichert und aus diesem abgeführt, wenn der Druck in der Zuleitung 24 sinkt.An illustrated in Figs. 1 and 2 gas pressure accumulator 10 has a cup-shaped Housing 12, which is closed by a cover 14. The interior of the Housing 12 is of a subsequent to the lid 14 metal bellows 16 and a gas-tight attached disc 18 in a gas space 20 and a fluid space 22nd divided. The gas space 20 is filled with a pressurized gas. The lid 14 is pierced by a supply line 24, through which the fluid space 22 a fluid is supplied when the pressure in the supply line 24 increases. The fluid is in the fluid space 22 stored and discharged from this when the pressure in the supply line 24 drops.

Das Gehäuse 12 hat eine zylinderförmige Außenwand 26 mit einer Längsachse 28. An die Außenwand 26 schließt eine scheibenförmige Stirnwand 30 an, in der koaxial eine Gewindebohrung 32 ausgebildet ist, durch die in den Gasraum 20 das Gas mit einem sogenannten Gasvordruck zugeführt werden kann. Die Gewindebohrung 32 ist mit einer Verschlußschraube 34 verschlossen, die auf einer Dichtscheibe 36 aufliegt.The housing 12 has a cylindrical outer wall 26 with a longitudinal axis 28. To the outer wall 26 includes a disc-shaped end wall 30, in the coaxial a threaded bore 32 is formed, through which in the gas space 20, the gas with can be supplied to a so-called gas supply pressure. The threaded bore 32 is closed with a screw plug 34 which rests on a sealing washer 36.

Der Deckel 14 weist einen scheibenförmigen Verschlußabschnitt 38 auf, der mittels eines daran am Umfang ausgebildeten Absatzes 40 in der Außenwand 26 des Gehäuses 12 zentriert und an dieser abgestützt ist. Der scheibenförmige Verschlußabschnitt 38 ist mit der Außenwand 26 durch eine Schweißnaht 42 gasdicht verbunden. The lid 14 has a disc-shaped closure portion 38 which by means of a circumferentially formed paragraph 40 in the outer wall 26 of the housing 12 centered and supported on this. The disc-shaped closure portion 38 is connected to the outer wall 26 by a weld 42 gas-tight.

Bei dem in Fig. 1 dargestellten Ausführungsbeispiel sind an der dem Innenraum des Gehäuses 12 zugewandten Seite des Verschlußabschnittes 38 koaxial ein Hohlzylinder 44 und ein Dorn 46 einstückig ausgebildet. An der Außenseite des Verschlußabschnittes 38 ist koaxial ein Anschluß 48 einstückig ausgebildet, der durch im wesentlichen axial gerichtete Bohrungen 50, 52 und 54 mit dem Innenraum des Gehäuses 12 verbunden ist.In the embodiment shown in Fig. 1 are at the the interior of the Housing 12 facing side of the closure portion 38 coaxial with a hollow cylinder 44 and a mandrel 46 integrally formed. On the outside of the closure portion 38 is coaxially a terminal 48 integrally formed by the in essential axially directed bores 50, 52 and 54 with the interior of the Housing 12 is connected.

Der Metallbalg 16 ist gefaltet, im wesentlichen zylinderförmig und an seinen beiden axialen Enden durch Schweißnähte 56 und 58 mit dem Verschlußabschnitt 38 bzw. der Scheibe 18 gasdicht verbunden.The metal bellows 16 is folded, substantially cylindrical and at its two axial ends through welds 56 and 58 with the closure portion 38 and the disc 18 connected gas-tight.

Die Scheibe 18 ist achsnormal gerichtet und mit einer koaxialen Stange 60 einstückig verbunden, in der eine axiale Bohrung 62 ausgebildet ist, mittels der die Stange 60 auf dem Dorn 46 geführt ist. An die Stange 60 schließt einstückig ein Kolben 64 an, dessen Durchmesser größer als der der Stange 60 ist.The disc 18 is directed normal to the axis and with a coaxial rod 60 in one piece connected, in which an axial bore 62 is formed, by means of which the rod 60th is guided on the mandrel 46. To the rod 60 integrally connects a piston 64, whose diameter is larger than that of the rod 60.

Am inneren Umfang des Hohlzylinders 44 sind zwei axial voneinander beabstandete, achsparallele Dichtflächen 66 und 68 ausgebildet, die axial gerichtet sind und je einen Dichtsitz bilden. Axial zwischen den Dichtflächen 66 und 68 ist eine Aussparung 70 am inneren Umfang des Hohlzylinders 44 ausgebildet, so daß dessen Durchmesser in diesem Bereich größer als der Durchmesser der Dichtsitze an den Dichtflächen 66 und 68 ist.At the inner circumference of the hollow cylinder 44 are two axially spaced apart, axially parallel sealing surfaces 66 and 68 are formed, which are axially directed and each form a sealing seat. Axial between the sealing surfaces 66 and 68 is a recess 70 formed on the inner circumference of the hollow cylinder 44, so that its Diameter in this area greater than the diameter of the sealing seats on the Sealing surfaces 66 and 68 is.

Der Kolben 64 weist eine Umfangsnut auf, in der eine Dichtung 72 in Form eines Dichtrings eingesetzt oder eingespritzt ist. Die Dichtung 72 ist so ausgebildet, daß sie mit der Dichtfläche 66 oder 68 zusammenwirkt und dadurch eine Ventilanordnung 74 bildet, die zweifach flüssigkeitsdicht abdichten kann.The piston 64 has a circumferential groove in which a seal 72 in the form of a Sealing ring is inserted or injected. The gasket 72 is formed to be cooperates with the sealing surface 66 or 68 and thereby a valve assembly 74th forms, which can seal two times liquid-tight.

In Fig. 1 ist der Metallbalg 16 in einer Stellung dargestellt, in der nahezu kein Fluid im Gasdruckspeicher 10 gespeichert ist, also der Druck im Fluidraum 22 seinen Minimalwert, den Gasvordruck, erreicht hat. Der Kolben 64 befindet sich dabei nahezu in einer Grundstellung, bei der die Dichtung 72 an der Dichtfläche 66 anliegt und an dieser abdichtet. Dadurch ist zwischen dem Kolben 64, dem Hohlzylinder 44 und dem Verschlußabschnitt 38 des Deckels 14 ein sogenannter Vorraum 76 geschaffen, der nur durch die Bohrung 52 mit dem Anschluß 48 verbunden, ansonsten aber abgeschlossen ist. Die Ventilanordnung ist also zwischen der Zuleitung 24 und dem Fluidraum 22 geschlossen. Da aus dem Fluidraum 22 kein Fluid in den Vorraum 76 übertreten kann, bleibt auch bei einem Absinken des Drucks am Anschluß 48 der Druck im Fluidraum 22 konstant und auf den Minimalwert begrenzt. Der Metallbalg 16 ist dadurch sicher gegen Beschädigung bei Druckabfall geschützt.In Fig. 1, the metal bellows 16 is shown in a position in which almost no fluid is stored in the gas pressure accumulator 10, so the pressure in the fluid space 22 its Minimum value, the gas form has reached. The piston 64 is here almost in a normal position, in which the seal 72 bears against the sealing surface 66 and seals at this. As a result, between the piston 64, the hollow cylinder 44th and the closure portion 38 of the lid 14 created a so-called vestibule 76, the only connected through the bore 52 to the terminal 48, otherwise but is complete. The valve assembly is thus between the supply line 24 and the fluid space 22 is closed. As from the fluid space 22 no fluid in the vestibule 76 can remain, even with a drop in pressure at port 48 of Pressure in the fluid space 22 constant and limited to the minimum value. The metal bellows 16 is thus safe against damage due to pressure drop protected.

Steigt der Druck am Anschluß 48 bzw. der Zuleitung 24, so wird auch der Druck im Vorraum 76 erhöht und der Kolben 64 axial bezogen auf Fig. 1 nach oben bewegt, wobei der Metallbalg 16 gelängt und der Gasraum 20 verkleinert wird. Im Bereich der Aussparung 70 kann das einströmende Fluid dabei den Kolben 64 umströmen und wirkt dadurch unmittelbar auf den Metallbalg 16 bzw. die Scheibe 18. Der steigende Fluiddruck bewegt den mit der Scheibe 18 verbundenen Kolben 64 dabei nahezu reibungsfrei im Bereich eines Hubweges X, der dem Betriebshub des Gasdruckspeichers 10 entspricht. Durch die Bohrung 54 kann dabei Fluid in die Bohrung 62 gelangen, so daß dort ein Druckausgleich stattfindet.If the pressure rises at the connection 48 or the supply line 24, then the pressure in Antechamber 76 increases and the piston 64 moves axially relative to FIG. 1, wherein the metal bellows 16 elongated and the gas space 20 is reduced. Around Recess 70, the inflowing fluid while the piston 64 flow around and acts directly on the metal bellows 16 and the disc 18. Der rising Fluid pressure moves the piston 18 connected to the piston 64 almost frictionless in the area of a stroke X, the operating stroke of the gas pressure accumulator 10 corresponds. Through the bore 54 can thereby fluid in the bore 62nd arrive, so that there takes place a pressure compensation.

Bei weiter ansteigendem Druck am Anschluß 48 gelangt bei einem sogenannten Maximaldruck im Fluidraum 22 der Kolben 64 mit seiner Dichtung 72 an die Dichtfläche 68 und dichtet dort ab. Der Kolben 64 befindet sich nahezu in seiner Endstellung und die Ventilanordnung 74 schließt nun wieder zwischen dem Fluidraum 22 und der Zuleitung 24 bzw. dem Vorraum 76 ab. Der Metallbalg 16 ist damit gegen Beschädigung durch Überdruck geschützt, da kein Fluid aus dem Vorraum 76 in den Fluidraum 22 überströmen kann.With further increasing pressure at the terminal 48 arrives at a so-called Maximum pressure in the fluid chamber 22 of the piston 64 with its seal 72 to the sealing surface 68 and seal off there. The piston 64 is almost in its end position and the valve assembly 74 now closes again between the fluid space 22 and the Supply line 24 and the vestibule 76 from. The metal bellows 16 is thus against damage protected by overpressure, since no fluid from the vestibule 76 in the fluid space 22 can flow over.

An den Dichtflächen 66 und 68 kann der Kolben 64 mit der Dichtung 72 je einen axialen Hubweg X1 bzw. X2 entlanggleiten. Während dieser Hubwege X1 und X2 bleibt die Abdichtung bestehen, während ein geringer Druckausgleich zwischen dem Fluidraum 22 und dem Vorraum 76 möglich ist. Auf diese Art können Elastizität und Wärmedehnung wie oben beschrieben ausgeglichen werden.At the sealing surfaces 66 and 68, the piston 64 with the seal 72 each slide along an axial stroke X 1 and X 2 . During these strokes X 1 and X 2 , the seal remains, while a low pressure equalization between the fluid chamber 22 and the vestibule 76 is possible. In this way, elasticity and thermal expansion can be compensated as described above.

Um zu verhindern daß der Kolben 64 die Dichtung 72 über die Dichtfläche 66 hinaus bewegt, ist im in Fig. 1 axial unteren, inneren Ende des Kolbens 64 eine Fase 78 ausgebildet und am Verschlußabschnitt 38 ein dem Kolben 64 gegenüberliegender Endanschlag 80, an dem der Kolben 64 definiert anliegen kann.To prevent the piston 64, the seal 72 beyond the sealing surface 66 addition moves, in Fig. 1 axially lower, inner end of the piston 64 is a chamfer 78th formed and the closure portion 38, a piston 64 opposite End stop 80, on which the piston 64 can abut defined.

Ferner ist im Bereich dieses Endanschlags 80 in den Verschlußabschnitt 38 eine Dichtung 82 eingesetzt, die zusammen mit einem am Kolben 64 gegenüberliegend ausgebildeten Dichtsitz 84 eine redundante Abdichtung des Kolbens 64 in der Grundstellung bildet. Die Dichtung 82 kann alternativ im Kolben 64 eingesetzt sein.Furthermore, in the region of this end stop 80 in the closure portion 38 a Seal 82 is used, which, together with one on the piston 64 opposite trained sealing seat 84 a redundant sealing of the piston 64 in the Basic position forms. The seal 82 may alternatively be inserted in the piston 64.

An der Stirnwand 30 ist innen ein Endanschlag 86 ausgebildet, gegen den die Scheibe 18 in der bezogen auf Fig. 1 oberen Endstellung des Kolbens 64 anliegt.On the end wall 30, an end stop 86 is formed inside, against which the Disc 18 in relation to FIG. 1 upper end position of the piston 64 abuts.

Die Fig. 2 zeigt ein Ausführungsbeispiel eines Gasdruckspeichers 10, der ähnlich dem in Fig. 1 dargestellten aufgebaut ist. Bei diesem Gasdruckspeicher 10 ist jedoch die Scheibe 18 mit der Stange 60 und einem Hohlzylinder 44' einstückig verbunden. Die Stange 60 ist in einer Bohrung 54' des Dorns 46 axial verschiebbar geführt und von einer Bohrung 62' durchsetzt, welche die Bohrung 50 mit dem Vorraum 76 verbindet. Am dem Hohlzylinder 44' zugewandten Ende ist mit dem Dorn 46 ein Kolben 64' einstückig ausgebildet.Fig. 2 shows an embodiment of a gas pressure accumulator 10, which is similar to is shown in Fig. 1 is constructed. In this gas pressure accumulator 10, however, is the Disc 18 integrally connected to the rod 60 and a hollow cylinder 44 '. The Rod 60 is axially slidably guided in a bore 54 'of the mandrel 46 and of a hole 62 'passes, which connects the bore 50 with the vestibule 76. At the hollow cylinder 44 'facing the end of the mandrel 46 is a piston 64' integrally formed.

Bei dieser Ausführungsform wird beim Hub der Scheibe 18 der Hohlzylinder 44' bewegt, während der Kolben 64' ortsfest bleibt. Ansonsten ist die Funktion der Ventilanordnung gleich der oben für Fig. 1 beschriebenen.In this embodiment, the stroke of the disc 18 of the hollow cylinder 44 ' moves while the piston 64 'remains stationary. Otherwise, the function of the Valve arrangement similar to that described above for Fig. 1.

Im Gegensatz zum Ausführungsbeispiel der Fig. 1 ist am Kolben 64' ein Endanschlag 80' ausgebildet. Ferner ist am Kolben 64' eine axial gerichtete Dichtung 82' angeordnet, die mit einem gegenüberliegenden Dichtsitz 84' an der Scheibe 18 eine redundante Abdichtung des Kolbens 64' in der Grundstellung bildet.In contrast to the embodiment of FIG. 1 is on the piston 64 'an end stop 80 'trained. Further, an axially directed seal 82 'is arranged on the piston 64', the one with an opposite sealing seat 84 'on the disc 18 is a redundant Seal the piston 64 'in the normal position forms.

Claims (8)

  1. A gas pressure accumulator (10) for a vehicle brake system having a housing (12), the interior of which is divided by metal bellows (16) and a disk (18) mounted to the metal bellows (16) in gas-tight manner into a gas-filled gas chamber (20) and a fluid chamber (22), wherein via a feed line (24) a fluid may under pressure be supplied to or removed from the fluid chamber (22), and provided between the fluid chamber (22) and the feed line (24) is a valve arrangement (74), which closes when the pressure in the feed line (24) drops below a minimum value and opens when the pressure exceeds the minimum value, wherein the metal bellows (16) performs a stroke movement (X) during supply and removal of the fluid by means of which the valve arrangement (74) is actuated, wherein the disk (18) is integrally connected with a rod (60, 60') in which an axial bore (62, 62') is formed, wherein the rod (60) by means of the axial bore (62) is guided so as to be axially slidable on a mandrel (46), or the rod (60') is guided so as to be axially slidable in a bore (54') of the mandrel (46), characterized in that a hollow cylinder (44, 44') is connected with the disk (18) or a closing portion (38) of the housing (12), and extends coaxially with the mandrel (46) and is disposed radially inside the essentially hollow-cylindrically designed metal bellows (16).
  2. Gas pressure accumulator according to claim 1, wherein a piston (64) is guided in the hollow cylinder (44).
  3. Gas pressure accumulator according to claim 1, wherein the hollow cylinder (44') is guided on a piston (64').
  4. Gas pressure accumulator according to one of claims 1 to 3, wherein a connection (48) that is connected with the interior of the housing (12) by bores (50, 52, 54) is formed on the outside of the closing portion (38).
  5. Gas pressure accumulator according to claim 2 or 3 and claim 4, wherein between the piston (64, 64'), the hollow cylinder (44, 44') and the closing portion (38) of the housing (12) or the disk (18) an admission chamber (76) is created that is connected with the connection (48) via a bore (52).
  6. Gas pressure accumulator according to claim 2 or 3, wherein the piston (64) integrally adjoins the rod (60) and the diameter of the piston (64) is greater than the diameter of the rod (60).
  7. Gas pressure accumulator according to claim 2 or 3, wherein the piston (64') is integrally connected with the mandrel (46) and the diameter of the piston (64) is greater than the diameter of the mandrel (46).
  8. A vehicle brake system having a gas pressure accumulator (10) according to one of the preceding claims.
EP02016285A 1999-11-11 2000-11-02 Vehicle braking system with a gas hydraulic accumulator Expired - Lifetime EP1251282B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19954326 1999-11-11
DE19954326A DE19954326B4 (en) 1999-11-11 1999-11-11 Vehicle brake system with a gas pressure accumulator
EP00981234A EP1228318B1 (en) 1999-11-11 2000-11-02 Vehicle braking system comprising a gas hydraulic accumulator

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP00981234.8 Division 2000-11-02
EP00981234A Division EP1228318B1 (en) 1999-11-11 2000-11-02 Vehicle braking system comprising a gas hydraulic accumulator

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EP1251282A2 EP1251282A2 (en) 2002-10-23
EP1251282A3 EP1251282A3 (en) 2003-07-02
EP1251282B1 true EP1251282B1 (en) 2005-10-26

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EP02016285A Expired - Lifetime EP1251282B1 (en) 1999-11-11 2000-11-02 Vehicle braking system with a gas hydraulic accumulator
EP00981234A Expired - Lifetime EP1228318B1 (en) 1999-11-11 2000-11-02 Vehicle braking system comprising a gas hydraulic accumulator

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EP (2) EP1251282B1 (en)
JP (2) JP2003514202A (en)
AT (2) ATE248994T1 (en)
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DE (3) DE19954326B4 (en)
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Publication number Publication date
ES2206332T3 (en) 2004-05-16
EP1251282A3 (en) 2003-07-02
ATE248994T1 (en) 2003-09-15
WO2001034984A3 (en) 2001-10-18
US6666529B2 (en) 2003-12-23
DE19954326A1 (en) 2001-05-23
ES2250552T3 (en) 2006-04-16
JP2003514202A (en) 2003-04-15
AU1855301A (en) 2001-06-06
EP1251282A2 (en) 2002-10-23
JP2003175819A (en) 2003-06-24
ATE307979T1 (en) 2005-11-15
EP1228318B1 (en) 2003-09-03
US6616247B2 (en) 2003-09-09
US20030038532A1 (en) 2003-02-27
US20020180260A1 (en) 2002-12-05
DE19954326B4 (en) 2006-06-29
DE50003583D1 (en) 2003-10-09
EP1228318A2 (en) 2002-08-07
WO2001034984A2 (en) 2001-05-17
DE50011469D1 (en) 2005-12-01

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