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WO1992001867A1 - Dispositif pour l'absorption des pulsations de pression - Google Patents

Dispositif pour l'absorption des pulsations de pression Download PDF

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Publication number
WO1992001867A1
WO1992001867A1 PCT/EP1991/001040 EP9101040W WO9201867A1 WO 1992001867 A1 WO1992001867 A1 WO 1992001867A1 EP 9101040 W EP9101040 W EP 9101040W WO 9201867 A1 WO9201867 A1 WO 9201867A1
Authority
WO
WIPO (PCT)
Prior art keywords
arrangement according
damping
inlet
pulsation
chamber
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.)
Ceased
Application number
PCT/EP1991/001040
Other languages
German (de)
English (en)
Inventor
Franz Fleck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Teves AG and Co OHG
Original Assignee
Alfred Teves 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 Alfred Teves GmbH filed Critical Alfred Teves GmbH
Publication of WO1992001867A1 publication Critical patent/WO1992001867A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • B60T8/40—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 comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4068—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 comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system the additional fluid circuit comprising means for attenuating pressure pulsations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/04—Devices damping pulsations or vibrations in fluids

Definitions

  • the invention relates to an arrangement for absorbing pressure pulsations and other vibrations in pressurized, in particular hydraulic, systems, with at least one damping chamber arranged in the pressurized consumer inflow with inlet and outlet bores.
  • Such an arrangement is known from DE 38 08 901 AI and DE 39 15 781 AI in hydraulic radial piston pump systems for motor vehicles. It is used to measure the pump-related pressure fluctuations in the output circuit of the pump, i.e. to reduce the degree of non-uniformity of the feed current to the consumer. These pressure fluctuations are ultimately transferred to the actuator, e.g. on the brake pedal of a motor vehicle when used in a power steering system.
  • the damping chambers of the known arrangements essentially have a cylindrical interior, which, due to its relatively large volume, serves as a collecting space for the hydraulic fluid and dampens the pressure fluctuations.
  • the invention is based on the object, starting from the arrangement described at the outset, of creating a damping chamber which can be used universally, possibly also be retrofitted and which ensures good and inexpensive noise and pulsation reduction.
  • the damping chamber has a substantially spherical or egg-shaped interior and a sound-absorbing multi-layer casing, and that the inlet and outlet bores are arranged opposite one another offset.
  • the cavity with a spherical to ovoid shape and offset inlet and outlet bores causes penetrating pulsations to be constantly reflected and broken and wipe each other out.
  • a multi-layer coating of the damping chamber is provided so that airborne and structure-borne noise cannot propagate freely from the pressure inlet side to the consumer side.
  • a particularly effective reduction in pulsation can be achieved according to a design feature of the invention in that three damping chambers are axially aligned in series and the inlet and outlet bores are each axially offset.
  • the arrangement is expediently such that the inlet bore of the damping chamber associated with the pressure generator has a relatively large cross section.
  • a particularly effective sheathing of the damping chambers results from the fact that the damping chambers are formed in axially successive blocks which are connected to one another via sealing arrangements, of which the two outer ones each have a pot-like extension running coaxially to one another.
  • To reinforce the radial Sound reduction is expediently provided between the pot-like extensions at least one axially extending annular space in which a negative pressure can be produced.
  • the only figure in the patent drawing shows three spherical cavities connected in series, the spherical chambers 1, 2, 3 of a damping body in a hydraulic system, which are surrounded by a multi-layer casing.
  • the ball chamber 1 is connected via a relatively large inlet bore 4 to a pressurized line via which the pressure pulsations or vibrations are transmitted. Due to the large inlet hole, the pressure connection from the pressure generator (e.g. pump) to the ball chamber 1 can be seen as a one-piece pressure supply chamber.
  • the pressure generator e.g. pump
  • the pulsating pressure medium therefore enters the damping body via the inlet bore 4, as indicated by the arrow.
  • the ball chamber 1 is connected via the output bore 5 to the input bore 6 of the ball chamber 2.
  • the ball chamber 2 is connected via the output bore 7 to the input bore 8 of the ball chamber 3.
  • the low-pulsation pressure medium emerges from the outlet 9 of the ball chamber 3 Damping body out and in the consumer inlet.
  • each ball chamber is - as can also be seen in the drawing - arranged axially offset from one another.
  • Pressure pulsations which are caused by a pressure generator (not shown), are introduced into the ball chamber 1 provided with the large inlet bore 4. A partial reduction of the incoming pressure pulsations takes place in this spherical chamber.
  • the effect of the spherical cavity consists in the fact that pressure pulsations that occur propagate on all sides. When they hit the cavity shell, they are reflected and reflected back according to their angle of incidence. This process is repeated continuously. It can be assumed that the majority of pulsation peaks meet pulsation troughs and thus cancel each other out.
  • the pressure pulsation from the pressure generator into the ball chamber 1 is already greatly reduced as a result of feedback, ie ' . also due to the reduced pressure pulsation in the pressure supply system itself, the breathing work is reduced backwards into the pressure generator. The airborne noise generated in this way is also reduced.
  • the ball chamber 1 therefore already results in a reduction in noise due to reduced breathing work inside and on the surface of the pressure generator.
  • the inlet and outlet bores 4 and 5 of the ball chamber 1 are staggered. This should also increase the absorption behavior.
  • the already damped, but still pulsating pressure medium enters the ball chamber 2 via the inlet bore 6.
  • the inlet and outlet bores 6 and 7 of this ball chamber 2 are also arranged offset for the reasons mentioned above.
  • this spherical chamber 3 primarily serves to largely eliminate direct pulsations (eg from hydraulic motors, cylinders, valves, etc.) coming from the consumer or indirectly caused pulsations (such as external forces acting on the aforementioned hydraulic components) .
  • the mode of operation is corresponding to that of the spherical chambers 1 and 2.
  • the multi-stage ball chamber arrangement according to the figure of the patent drawing therefore causes a very strong damping of the pressure pulsations in the pressure medium.
  • the embodiment shown in the patent drawing is to be understood as an exemplary embodiment.
  • the embodiment of the pulsation damping body according to the invention can also consist of a single ball in its simplest form. This ball can, if necessary, be designed somewhat modified in accordance with the specific requirements.
  • the spherical chambers do not necessarily have to be arranged axially one behind the other if, for example, specific requirements (installation conditions) only allow a different body contour.
  • the spherical chambers 1 to 3 are formed in four blocks of the damping body, which are connected to one another via sealing rings 13.
  • the ball chamber 1 is contained in the head part 10, which preferably consists of light metal, and the inner block 11, which is preferably formed by a multilayer plastic material.
  • the ball chamber 2 is formed in a corresponding manner in the blocks 11 and 12, the latter also preferably being constructed from a multilayer plastic.
  • the spherical chamber 3 is finally located in the blocks 12 and 15, the latter being pot-shaped and preferably also consisting of a multilayer plastic.
  • the blocks are held in a pot-shaped receptacle 16 made of light metal, which is connected to the block 15 via an adhesive 17.
  • ring channels 18 which can be connected to a vacuum generator via a connection 14.
  • the vacuum generator can be, for example, the intake manifold or the carburetor of a motor vehicle or the intake constriction of a pump, etc.
  • the described sheathing of the ball chamber serves to ensure that it comes from the pulsation generator Structure-borne noise is not passed on via the damping body.
  • the housing of the damping body has a multilayer structure both in the direction of flow and radially outward. In the case of an axial pass, for example, the structure-borne noise must first pass through a metal layer.
  • the rate of propagation of the pulsations being greatly reduced or changed.
  • the structure-borne noise that still penetrates into the spherical chambers or the structure-borne noise that is still indirectly caused here by pulsation / breathing work is also reduced in the radial direction.
  • the airborne noise occurring is primarily absorbed by the vacuum chamber 18, which surrounds the spherical chambers in a ring.
  • This vacuum chamber also has a dampening effect on structure-borne noise.
  • the structure-borne sound pressure waves must penetrate a total of five different layers (including the spherical chamber shells). The number and sequence of the layers is to be determined and determined specifically by the person skilled in the art in a corresponding investigation for the respective application.
  • the basic principle of the multi-layer cladding therefore consists in the fact that structure-borne and airborne noise that occurs has to change its speed of sound propagation as the different layers pass through; it is also broken at the interfaces. He therefore loses energy. This effect is supported by the substantial absence of air in the vacuum chamber 18. In addition, the stratification can influence the frequency of the sound, which nevertheless penetrates outwards, in such a way that it is more bearable for the user.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Pipe Accessories (AREA)
  • Liquid Crystal (AREA)

Abstract

Dans des systèmes sollicités par des fluides sous pression, notamment des systèmes hydrauliques, il y a production de variations de pression inhérentes au système, dans le circuit d'alimentation, ou de bruits gênants pour l'utilisateur du système. Pour l'amortissement de ces pulsations de pression et des bruits, l'invention prévoit, comme chambre d'insonorisation du bruit, un espace creux de configuration sphérique à ovoïde, doté d'une enveloppe multicouche insonorisante, ainsi que de trous décalés d'entrée et de sortie. Cette chambre d'insonorisation est d'une installation universelle ou, le cas échéant, peut être également mise en place ultérieurement et permet d'obtenir une réduction satisfaisante et bon marché du bruit et des pulsations. D'autres formes d'exécution avantageuses de l'invention concernent une configuration appropriée de la chambre d'insonorisation et de son enveloppe.
PCT/EP1991/001040 1990-07-26 1991-06-06 Dispositif pour l'absorption des pulsations de pression Ceased WO1992001867A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DEP4023709.5 1990-07-26
DE19904023709 DE4023709A1 (de) 1990-07-26 1990-07-26 Vorrichtung zur absorption von druckpulsationen

Publications (1)

Publication Number Publication Date
WO1992001867A1 true WO1992001867A1 (fr) 1992-02-06

Family

ID=6411029

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1991/001040 Ceased WO1992001867A1 (fr) 1990-07-26 1991-06-06 Dispositif pour l'absorption des pulsations de pression

Country Status (4)

Country Link
EP (1) EP0494275A1 (fr)
JP (1) JPH05501142A (fr)
DE (1) DE4023709A1 (fr)
WO (1) WO1992001867A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2686955A1 (fr) * 1992-02-04 1993-08-06 Automotive Prod France Dispositif d'amortissement pour mecanisme d'actionnement hydraulique.
US20160001754A1 (en) * 2014-07-02 2016-01-07 Mando Corporation High pressure accumulator of brake system
CN108731871A (zh) * 2017-10-26 2018-11-02 江苏核电有限公司 一种大气压取压装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19508096A1 (de) * 1995-03-08 1996-09-12 Trw Fahrwerksyst Gmbh & Co Lenkventil
EP0791524B1 (fr) * 1996-02-22 1998-11-04 TRW Fahrwerksysteme GmbH & Co. KG Soupape de direction
DE102004049512B4 (de) * 2004-10-11 2013-11-28 Bürkert Werke GmbH Modulares Gehäusesystem für fluidische Steuer- und Regelgeräte

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1170212A (fr) * 1955-11-14 1959-01-12 Dowty Equipment Ltd Atténuateur de pulsations hydrauliques
DE1242420B (de) * 1962-07-18 1967-06-15 Wilhelm S Everett Pulsationsdaempfer und Fluessigkeitsabscheider fuer stroemende Gase
US3731709A (en) * 1971-06-01 1973-05-08 Fluid Kinetics Corp Liquid pulsation dampener
DE3209296A1 (de) * 1982-03-13 1983-09-29 Balcke-Dürr AG, 4030 Ratingen Anordnung mit einem pulsationsdaempfer
DE3807954A1 (de) * 1988-03-10 1989-09-21 Kugelfischer G Schaefer & Co Daempfungselement

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1221061B (de) * 1958-04-21 1966-07-14 Applic Mach Motrices Einrichtung zum Daempfen von Druckstoessen in Fluessigkeitsleitungen mit einer ein Gasvolumen einschliessenden elastischen Blase
DE1956254A1 (de) * 1969-11-08 1971-05-13 Daimler Benz Ag Mit einem Druckregler ausgestattete Druckluftanlage fuer Fahrzeuge
US3621882A (en) * 1970-02-25 1971-11-23 Harry P Kupiec Inline, through-flow pressure compensator and accumulator
DE2254032A1 (de) * 1972-11-04 1974-05-16 Bosch Gmbh Robert Druckspeicher
DE2902995A1 (de) * 1979-01-26 1980-09-04 Sperry Vickers Fluessigkeitsschalldaempfer
DE2910025A1 (de) * 1979-03-14 1980-09-18 Wagner Gmbh J Druckspitzenkompensator fuer pulsierende fluessigkeitsstroeme
DE3146454A1 (de) * 1981-11-24 1983-06-01 Robert Bosch Gmbh, 7000 Stuttgart Element zum daempfen von druckschwingungen in hydraulischen systemen
DE3147000A1 (de) * 1981-11-27 1983-06-30 Wabco Westinghouse Fahrzeugbremsen GmbH, 3000 Hannover Wegeventil
DE3326802C2 (de) * 1983-07-26 1986-03-20 Festo KG, 7300 Esslingen Anschlußblock
DE3808901C2 (de) * 1988-03-17 1997-03-13 Teves Gmbh Alfred Radialkolbenpumpe, insbesondere für Kraftfahrzeug-Bremsanlagen mit ABS
DE3915781A1 (de) * 1988-05-18 1989-11-30 Zahnradfabrik Friedrichshafen Radialkolbenpumpe
JPH03502829A (ja) * 1988-12-17 1991-06-27 アルフレツド・デヴエス・ゲー・エム・ベーハー 液圧ポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1170212A (fr) * 1955-11-14 1959-01-12 Dowty Equipment Ltd Atténuateur de pulsations hydrauliques
DE1242420B (de) * 1962-07-18 1967-06-15 Wilhelm S Everett Pulsationsdaempfer und Fluessigkeitsabscheider fuer stroemende Gase
US3731709A (en) * 1971-06-01 1973-05-08 Fluid Kinetics Corp Liquid pulsation dampener
DE3209296A1 (de) * 1982-03-13 1983-09-29 Balcke-Dürr AG, 4030 Ratingen Anordnung mit einem pulsationsdaempfer
DE3807954A1 (de) * 1988-03-10 1989-09-21 Kugelfischer G Schaefer & Co Daempfungselement

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2686955A1 (fr) * 1992-02-04 1993-08-06 Automotive Prod France Dispositif d'amortissement pour mecanisme d'actionnement hydraulique.
US20160001754A1 (en) * 2014-07-02 2016-01-07 Mando Corporation High pressure accumulator of brake system
CN105270373A (zh) * 2014-07-02 2016-01-27 株式会社万都 制动系统的高压蓄能器
US9522660B2 (en) * 2014-07-02 2016-12-20 Mando Corporation High pressure accumulator of brake system
CN108731871A (zh) * 2017-10-26 2018-11-02 江苏核电有限公司 一种大气压取压装置
CN108731871B (zh) * 2017-10-26 2024-04-09 江苏核电有限公司 一种大气压取压装置

Also Published As

Publication number Publication date
DE4023709A1 (de) 1992-01-30
EP0494275A1 (fr) 1992-07-15
JPH05501142A (ja) 1993-03-04

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