EP1987254A1 - Accumulateur de pression, en particulier amortisseur de pulsations - Google Patents

Accumulateur de pression, en particulier amortisseur de pulsations

Info

Publication number
EP1987254A1
EP1987254A1 EP06818509A EP06818509A EP1987254A1 EP 1987254 A1 EP1987254 A1 EP 1987254A1 EP 06818509 A EP06818509 A EP 06818509A EP 06818509 A EP06818509 A EP 06818509A EP 1987254 A1 EP1987254 A1 EP 1987254A1
Authority
EP
European Patent Office
Prior art keywords
pressure accumulator
fluid
metal bellows
accumulator according
working
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.)
Granted
Application number
EP06818509A
Other languages
German (de)
English (en)
Other versions
EP1987254B1 (fr
Inventor
Markus Lehnert
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.)
Hydac Technology GmbH
Original Assignee
Hydac Technology 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 Hydac Technology GmbH filed Critical Hydac Technology GmbH
Publication of EP1987254A1 publication Critical patent/EP1987254A1/fr
Application granted granted Critical
Publication of EP1987254B1 publication Critical patent/EP1987254B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F15B1/021—Installations or systems with accumulators used for damping
    • 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
    • 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
    • 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

Definitions

  • Pressure accumulator in particular pulsation damper
  • the invention relates to a pressure accumulator, in particular pulsation damper, with a storage housing which defines a longitudinal axis and an inflow opening and an outflow opening for a fluid, wherein two working spaces, in particular a gas space for a working gas and a fluid cavities, within the storage housing fluid-tight, in particular gas-tight, are separated by a bellows-like separating member and the separating member is connected at its one end with a housing fixed conclusion of the gas space forming lid and at its other end with an axially movable piston housing in the storage housing, which forms a movable closure of the gas space, so that Working movements of the piston part effect volume changes of the work spaces adjacent to the separating element.
  • Pressure accumulator of this type are known, cf. DE 10 2004 004 341 A1. Such pressure accumulators are primarily used for damping pressure fluctuations in hydraulic systems in order to protect measuring and control devices, filters and other components integrated in the system from harmful pulsations.
  • a preferred field of application is the use as a pulsation damper in the injection system of internal combustion engines, in particular large diesel engines. on ships or in cogeneration plants.
  • Pressure fluctuations occur both in the fuel supply system and in the fuel return system, the frequency and severity of the pulsations being determined by the sequence of injection processes, the removal of fuel from the system, the compression, the injection by means of high-pressure injection pumps and the reopening connect to the system.
  • this frequency is for example 40 Hz at a speed of 600 revolutions / minute.
  • pressure peaks of more than 50 bar may occur.
  • the invention has for its object to provide a pressure accumulator, which is characterized despite a compact design by a particularly good damper effect.
  • an essential inventive feature over the prior art is that an in-line construction is implemented in which both fluid connections, the inlet opening and the outflow opening, lie on one axis.
  • the invention results in a shorter overall length and thus the desired compact design.
  • the in-line design also allows easier and space-saving installation. For example, if the storage enclosure has a cylindrical shape, after installation, the accumulator will appear like a conduit interface that only differs in diameter from the base conduit. Since no bending / torsion moments are exerted by the pressure accumulator on the line during in-line installation, it may be possible to reduce the number of fastening elements.
  • a metal bellows with a plurality of superimposed folds or membrane pairs is provided as the separating member, which limits the gas space between the lid and the piston part in its interior.
  • a metal bellows occur virtually no gas losses.
  • suitable metals for example non-ferrous steel, there are no problems with aggressive fluids such as diesel oil, heavy oil or biofuels. Also, increased fuel temperatures are not annoying, since corresponding metallic materials are resistant to temperatures well above 200 ° Celsius. As the metal bellows Welded connections are provided, resulting in a gas-tight seal without additional seals.
  • the piston part has, on its side adjoining the fluid space, a cavity which increases the volume of the fluid space. If in this case the arrangement is made such that the piston part is cup-shaped with a circular cylindrical side wall extending into the circular cylindrical interior of the metal bellows along the inside of its folds with correspondingly large immersion depth corresponding to the working movements of the piston part, the enlargement of the Volume of the fluid space at the same time accompanied by a reduction in the volume of the gas space. This results in several advantages.
  • the choice of the depth of the "pot” makes it possible to adapt the volume ratio of gas space to fluid space according to the respective working conditions, and on the other hand there is the particular advantage that the length of the metal bellows is chosen to be sufficiently long even if the volume of the gas space is desirably small This allows the bellows to be within tolerable material tensions when performing alternating motions so that it can perform as large a stroke as possible with as many repeats as possible without the need for a backlash Operating safety would be at risk.
  • the storage housing is a circular cylindrical tubular body in which the metal bellows is concentrically received to form an annular space between the inner wall of the tubular body and the outside of the metal bellows and the annular space forms part of the flow path of the fluid between inflow and outflow.
  • the inner diameter of the tubular body is chosen to be greater than the outer diameter of the metal bellows, the Lich- th cross section of the flow path formed by the annular space is equal to or greater than the clear cross section of inflow and outflow, then the largest possible fluid flow rates can be without realizing significant throttling.
  • the lid of the metal bellows is fixed to the inner wall of the tubular body via a support structure whose structural elements are designed with a view to minimizing throttling at the flow path between annulus and adjacent outflow opening.
  • the support structure may have a fixed to the inner wall of the tubular body retaining ring, with which the lid of the metal bellows is connected via extending from the side edge of the lid to the retaining ring mounting rods.
  • a stop device for cooperation with the piston member is present.
  • the stop means may also be formed by a structure whose structural elements are selected with a view to minimizing the restriction of the flow path caused by them.
  • a fixed to the inner wall of the tubular body retaining ring and at least one of the interior of the retaining ring spanning mounting rod may be provided.
  • the gas space may be filled with an additional amount of an alcohol, preferably ethylene glycol.
  • an alcohol preferably ethylene glycol.
  • a protective function for the metal bellows i. Before the piston part, for example in the case of overpressure in the fluid system, strikes against the lid of the metal bellows, a protective fluid cushion is formed between the piston part and the cover.
  • FIG. 1 is a longitudinal section of an embodiment of the pressure accumulator according to the invention.
  • Fig. 2 is a perspective oblique view only provided in the interior of the storage enclosure of the embodiment of Fig. 1 Damper unit, seen substantially in the direction indicated in Fig. 1 by arrow II, and
  • Fig. 3 is a perspective view corresponding to FIG. 2 oblique view of the damper unit, but seen substantially in the direction indicated in Fig. 1 with arrow III viewing direction.
  • the illustrated in the drawing embodiment of the pressure accumulator according to the invention which is used as a pulsation damper, has as a storage housing a circular cylindrical tubular body 1 with a longitudinal axis 3 on.
  • the tubular body 1 has on its inner wall 5 narrow annular grooves 7 as a seat for below to be described snap rings and each an internal thread 9 at both end regions.
  • a storage lid 11 is screwed at both ends, both of which are of the same design and sealed by a respective sealing element 13 on the tubular body 1.
  • the left in the figure memory cover 11 has a central inflow opening 15, while the right in the figure memory cover 11 has a corresponding outflow opening 17 for the fluid whose pressure fluctuations are to be damped.
  • damper unit In concentric with the longitudinal axis 3 located arrangement is in the interior of the tubular body 1 in Figs. 2 and 3 separately shown damper unit, which is designated in the latter figures as a whole with 19.
  • An essential part of the damper unit is a metal bellows 21 in the form of a bellows circular-cylindrical shape, which is shown in Fig. 1 in a fully extended state, the largest volume of the im
  • gas space 23 corresponds inside the metal bellows 21 located gas space 23 corresponds.
  • a membrane bellows not shown in more detail, which has membrane pairs arranged in juxtaposition instead of folds arranged one above the other.
  • one end 25 of the metal bellows 21 is welded to a cover 27.
  • the metal bellows 21 is welded to a piston part 31, which forms a movable closure of the gas space 23 and can perform an axial working movement in the storage housing, which leads to volume changes of the gas space 23 and of the fluid chamber 33 surrounding the damper unit 19.
  • the cover 27 is fixed to the inner wall 5 of the tubular body 1 via a support structure.
  • This support structure has a retaining ring 35, which is secured by means of a snap ring 37 which sits in the already mentioned annular groove 7.
  • the retaining ring 35 in turn is connected via attachment rods 39 to the side edge of the lid 27.
  • the piston member 31 has the shape of a pot, the circular cylindrical side wall 41 extends into the interior of the metal bellows 21, wherein the immersion depth in the interior of the piston position during the working movement of the piston member 31 is dependent ,
  • the piston part 31 in the illustration of Fig. 1 the largest volume of the gas space 23 corresponding end position, wherein the piston member 31 rests with its open pot edge of rods 43 which form part of an anchor device.
  • This stop device is formed by a similar structure, as it is also used as a support structure for the cover 27, ie a retaining ring 45 is secured by means of a snap ring 47 in the annular groove 7, wherein the rods 43 in a similar manner as the mounting rods 39 on Retaining ring 35, extending from the inner edge of the retaining ring 45.
  • the lid 27 has a central Fiillan gleich 49, via which the gas space 23 can be provided with a pre-filling, which consists of the working gas, namely N 2 , and an additional amount of an alcohol, preferably ethylene glycol.
  • the two storage lids 11 have only one opening, namely inflow opening 15 and outflow opening 17, a large opening cross-section can be provided, so that large flow rates can be achieved.
  • the inner diameter of the tubular body 1 and the outer diameter of the metal bellows 21 are selected such that a sufficiently large annular space 51 is available as part of the flow path belonging to the fluid space 33.
  • the components of the support structure for the cover 27 are chosen so that no significant impediment to the flow path is given, d. H.
  • Both the retaining ring 35 and the mounting rod 39 are, as can be seen from the figures, slim, so that the outer edge of the lid 27 can be flowed around relatively unhindered.
  • the storage housing is formed by a simple tubular body 1 and the housing closure by means of the same trained memory cover 11, results in a particularly simple and inexpensive production.
  • the damper unit 19 can be prefabricated as a unit that can be used as a whole in the tubular body 1 and fixed by means of snap rings 37, 47, there is also a particularly simple installation.
  • the prefabricated as a unit damper unit exists in particular from the actual metal bellows 21, as well as the piston member 31 and the retaining ring 35th
  • the piston member 31 In the pre-filled with gas state, the piston member 31 is supported on the stopper 43 with their attachment rods and the metal bellows 21 is so far in its maximum extension. In this condition, it is designed to withstand the internal gas pre-charge pressure in any case. In all other operating conditions, the metal bellows 21 is in a largely pressure-balanced state. Depending on the system pressure and the prevailing gas temperature between the lower and upper extreme point, it will be able to dampen or eliminate all pressure fluctuations for which it is designed to absorb or dispense liquid. The working principle then corresponds to that of a classic hydropneumatic pressure accumulator in the damper insert.
  • the stop device 43 with its attachment rods serves to support the piston part 31 as far as the system pressure drops below the pre-charge pressure inside the metal bellows assembly formed by the components metal bellows 21, piston part 31, retaining ring 35 and (gas) filling connection, which is the case, for example Prefilling the metal bellows 21 can be done with nitrogen.
  • the support of the free end face of the piston part 31 allows a free flow of the storage device, even if the system pressure should be less than the pre-charge pressure; In any case, the piston part 31 can not obstruct the fluid opening 15 in the cover 11.

Landscapes

  • 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)

Abstract

L'invention concerne un accumulateur de pression, en particulier un amortisseur de pulsation, qui présente un boîtier d'accumulateur (1) qui définit un axe longitudinal (3) et qui présente une ouverture d'entrée (15) et une ouverture de sortie (17) pour un fluide. Deux espaces de travail, en particulier un espace (23) pour un gaz de travail et un espace (33) pour un fluide sont séparés l'un de l'autre de manière étanche aux fluides et en particulier étanche aux gaz par un organe de séparation (21) en forme de soufflet disposé à l'intérieur du boîtier (1) de l'accumulateur. L'organe de séparation (21) est relié par une extrémité (25) à un couvercle (27) qui forme une fermeture de l'espace pour gaz (23) fixée sur le boîtier et par son autre extrémité (29) à une pièce en piston (31) qui peut être déplacée axialement dans le boîtier (1) de l'accumulateur et qui forme une fermeture mobile de l'espace pour gaz (23) de telle sorte que des déplacements de travail de la pièce en piston (31) entraînent des modifications de volume des chambres de travail adjacentes à l'organe de séparation (21). L'accumulateur de pression est caractérisé en ce que l'ouverture d'entrée (15) et l'ouverture de sortie (17) sont prévues respectivement sur l'une et sur l'autre extrémités du boîtier d'accumulateur (1) opposées dans la direction axiale, de telle sorte que le boîtier d'accumulateur (1) puisse être traversé par le fluide dans le sens de sa longueur et dans la direction du déplacement de travail de la pièce en piston (31).
EP06818509A 2006-02-22 2006-11-14 Accumulateur de pression, en particulier amortisseur de pulsations Not-in-force EP1987254B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006008175A DE102006008175A1 (de) 2006-02-22 2006-02-22 Druckspeicher, insbesondere Pulsationsdämpfer
PCT/EP2006/010885 WO2007098795A1 (fr) 2006-02-22 2006-11-14 Accumulateur de pression, en particulier amortisseur de pulsations

Publications (2)

Publication Number Publication Date
EP1987254A1 true EP1987254A1 (fr) 2008-11-05
EP1987254B1 EP1987254B1 (fr) 2012-09-12

Family

ID=37672249

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06818509A Not-in-force EP1987254B1 (fr) 2006-02-22 2006-11-14 Accumulateur de pression, en particulier amortisseur de pulsations

Country Status (8)

Country Link
US (1) US8176940B2 (fr)
EP (1) EP1987254B1 (fr)
JP (1) JP5074426B2 (fr)
KR (1) KR101304186B1 (fr)
CN (1) CN101384824B (fr)
DE (1) DE102006008175A1 (fr)
DK (1) DK1987254T3 (fr)
WO (1) WO2007098795A1 (fr)

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Publication number Priority date Publication date Assignee Title
RU2383785C1 (ru) * 2008-10-09 2010-03-10 Александр Анатольевич Строганов Гидропневматический аккумулятор со сжимаемым регенератором
CN102248489B (zh) * 2010-05-21 2013-05-29 中芯国际集成电路制造(上海)有限公司 一种脉动缓冲器及研磨液供应系统
EP2610881B1 (fr) * 2011-12-28 2014-04-30 Siemens Aktiengesellschaft Compensateur de pression pour dispositif sous-marin
US9677519B2 (en) * 2013-08-27 2017-06-13 Kia Motors Corporation Device for decreasing fuel pulsation of LPG vehicle
DE102014010006A1 (de) * 2014-07-05 2016-01-07 Hydac Technology Gmbh Hydropneumatischer Druckspeicher
CN104265700A (zh) * 2014-09-15 2015-01-07 邢宇 用金属波纹管式蓄压器代替胆式蓄压器和活塞式蓄压器
EP3306109B1 (fr) * 2015-05-29 2022-04-27 Eagle Industry Co., Ltd. Accumulateur de type à soufflet métallique
DE102016003153A1 (de) * 2016-03-15 2017-09-21 Hydac Technology Gmbh Speichervorrichtung und hydropneumatische Federung
FR3060533B1 (fr) * 2016-12-19 2025-04-11 Safran Aircraft Engines Accumulateur sur une ligne de carburant d'aeronef
CN107939834A (zh) * 2017-11-16 2018-04-20 中国航空工业集团公司北京航空精密机械研究所 一种抑制压力波动的超精密机床液压系统
USD893678S1 (en) 2018-02-05 2020-08-18 Blacoh Fluid Controls, Inc. Valve
US11346374B2 (en) * 2020-09-08 2022-05-31 Blacoh Fluid Controls, Inc. Fluid pulsation dampeners
US11549523B2 (en) 2021-04-27 2023-01-10 Blacoh Fluid Controls, Inc. Automatic fluid pump inlet stabilizers and vacuum regulators
CN115773192B (zh) * 2022-12-21 2024-10-15 北京航空航天大学 蓄压器以及火箭发动机输送系统
CN117536733B (zh) * 2023-10-19 2024-08-13 北京天兵科技有限公司 一种大型液体运载火箭pogo抑制系统及输送系统
CN117869117B (zh) * 2023-12-26 2024-07-30 北京天兵科技有限公司 一种蓄压器及运载火箭的推进剂输送系统

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US3424202A (en) * 1966-09-08 1969-01-28 Calumet & Hecla Dual bellows compensator
JPS5059811A (fr) 1973-09-28 1975-05-23
JPS547615A (en) 1977-06-20 1979-01-20 Kenei Terada Pressure baffler
JPH02225802A (ja) * 1989-02-27 1990-09-07 Nhk Spring Co Ltd アキュムレータ
JPH02266101A (ja) * 1989-04-05 1990-10-30 Nhk Spring Co Ltd アキュムレータ
US5205326A (en) * 1991-08-23 1993-04-27 Hydraulic Power Systems, Inc. Pressure response type pulsation damper noise attenuator and accumulator
DE29507077U1 (de) * 1995-04-27 1995-06-22 GEA Finnah GmbH, 48683 Ahaus Pulsationsdämpfer für Rohrleitungen für strömende Medien
DE102004004341A1 (de) * 2004-01-29 2005-08-18 Hydac Technology Gmbh Druckspeicher, insbesondere Pulsationsdämpfer
JP2006194367A (ja) * 2005-01-14 2006-07-27 Nok Corp 水撃防止装置

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Also Published As

Publication number Publication date
WO2007098795A1 (fr) 2007-09-07
DE102006008175A1 (de) 2007-08-23
KR20090035464A (ko) 2009-04-09
KR101304186B1 (ko) 2013-09-06
EP1987254B1 (fr) 2012-09-12
CN101384824B (zh) 2011-01-12
US8176940B2 (en) 2012-05-15
DK1987254T3 (da) 2012-10-01
JP5074426B2 (ja) 2012-11-14
JP2009527706A (ja) 2009-07-30
CN101384824A (zh) 2009-03-11
US20100307146A1 (en) 2010-12-09

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