EP1685323B1 - Vorrichtung zum dämpfen von druckstössen - Google Patents

Vorrichtung zum dämpfen von druckstössen Download PDF

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Publication number
EP1685323B1
EP1685323B1 EP04790081A EP04790081A EP1685323B1 EP 1685323 B1 EP1685323 B1 EP 1685323B1 EP 04790081 A EP04790081 A EP 04790081A EP 04790081 A EP04790081 A EP 04790081A EP 1685323 B1 EP1685323 B1 EP 1685323B1
Authority
EP
European Patent Office
Prior art keywords
piston
housing
further piston
connecting piece
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
EP04790081A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1685323A1 (de
Inventor
Norbert Weber
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 EP1685323A1 publication Critical patent/EP1685323A1/de
Application granted granted Critical
Publication of EP1685323B1 publication Critical patent/EP1685323B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0041—Means for damping pressure pulsations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention relates to a device for damping pressure surges in a fluid with a housing and a longitudinally movable against the biasing force of a spring accumulator in the housing piston according to the feature configuration of the preamble of claim 1.
  • the devices in question include the so-called hydraulic accumulators, one of the main tasks of hydraulic accumulators being to take up certain volumes of pressurized fluid from a hydraulic system and, if necessary, to return them to the system. Since the fluid is under pressure, the hydraulic accumulators are treated as pressure vessels and must be designed for the maximum operating pressure, taking into account the acceptance standards. For volume compensation in the hydraulic accumulator and the associated energy storage, the hydraulic fluid in the hydraulic accumulator is weighted or spring loaded or charged with gas. There is always a balance between the pressure of the pressure fluid and the weight of the spring or the back pressure generated by the gas. In most hydro plants hydropneumatic, so gas-loaded memory are used with separating element, which differs depending on the design of the separating element between bladder, piston and diaphragm accumulators.
  • the hydropneumatic accumulator mentioned have to fulfill a variety of tasks in a hydraulic system and, for example, in addition to the aforementioned energy storage for damping of mechanical shocks and pressure shock absorption in the hydraulic system to be involved.
  • hydraulic pumps such as positive displacement pumps
  • pulsations occur in the volume flow, these pulsations cause not only noise but also vibrations, which can lead to damage to the entire hydraulic system.
  • the aforementioned hydraulic, in particular positive displacement pumps are also used in the so-called.
  • Common rail technology in the field of diesel engines.
  • Newer developments of the third generation rely on the piezo technology for the injection systems for the diesel fuel.
  • the newly developed piezo inline injectors for the third common-rail generation (see VDI - News No. 33 of August 15, 2003) use piezo actuator modules that use coupler modules on switching valves and these in turn on a nozzle module of the fuel Injection system act, wherein the outstanding hydraulic speed of the system results from the high degree of integration of the inline injector, ie from the vicinity of the piezo package to the nozzle needle in the tip of the injector.
  • the moving masses of the new systems were reduced from 16g to 4g, whereby moving mass means the mass of the nozzle needle and the fuel filling the control chamber.
  • very high system pressures are necessary, which reach up to the order of 2200 bar.
  • the pertinent system pressure is from the said hydraulic pump, in particular positive displacement pump to build up with the described disadvantage of the occurring pressure and Pulsationsstête. If these pressure surges are passed on to the injector system, this can be too critical System conditions lead to failure of the piezo-injector system and injection system. If one knows what is known (cf.
  • a further device for damping pressure pulsations in a fluid system in particular in a fuel system of an internal combustion engine, wherein the known device comprises a housing in which at least one working space is present. This is connected to the fluid system and is partially limited by at least one movable wall element in the form of a metal membrane, which is set stationary in the housing at the edge. This wall element is operatively connected to a first spring means and to be able to smooth pressure pulsations even with variable pressure in the fluid system, it is provided that the device comprises at least a second movable wall element, which limits a second working space and also consists of an edge fixed in the housing metal membrane.
  • the first spring device is arranged between the two wall elements in the form of the membranes and operatively connected to both. Further, a throttle device is provided, via which the second working space is connected to the fluid system.
  • a generic device for damping pressure surges in a fluid comprising a housing and a longitudinally movable piston against the biasing force of a spring accumulator in the housing, one piston cooperating with another piston, which is guided longitudinally displaceable in a connecting piece of the housing, wherein in operation of the device, the piston in each displacement position of the other piston exerts on this a compressive force and wherein the further piston is formed in the manner of a punch.
  • the two pistons are mechanically connected to each other, that is, a piston is an integral part of the other piston, to induce the damping of the guided in the housing first piston is permanently supported on the compression spring assembly. Due to the one-piece construction of the two mentioned pistons it is sufficient that for a captive for the other piston, the first piston can be supported on the front side of the fitting and insofar outside the continuous housing opening in case of need.
  • a comparable arrangement in the form of a single-piston solution with different piston diameters on opposite sides of the single piston arrangement is also due to the US 2003/183197 A1 demonstrated. As far as the damping of pressure surges at very high system pressures, these known solutions leave nothing to be desired.
  • the present invention seeks to provide a device for damping pressure surges available, with which it is possible, even at very high system pressures to 2200 bar occurring pressure surges, caused by a hydraulic pump, in particular diesel fuel pump, so To dampen and / or smooth out any harmful force discharges into a piezo injector system the common rail technology takes place.
  • This object is achieved by a device having the features of claim 1 in its entirety.
  • the one piston is larger in diameter by a multiple than the diameter of the other piston and it has been shown that an inhibiting driving operation with the piston can be achieved by the pertinent arrangement. Especially Verkantungsvortician the other piston in the connecting piece of the housing are avoided by its separate, independent guidance so.
  • the further piston is machined, in particular lapped, on the outer peripheral side such that a metallically dense gap is achieved at least between parts of the outer circumference and the further piston on the inner wall of the housing opening.
  • the further piston may be provided on the outer peripheral side with ring or lubrication grooves.
  • a leakage opening arranged in the housing opens into the fluid space between the pistons, then the diesel medium, which nevertheless penetrates the interior of the housing, can, in the form of a return bore for leak oil depressurized in the block towards the tank or leakage side.
  • At least one helical spring designed as a compression spring and / or a compressed gas as a spring accumulator.
  • the use of a pure compressed gas may entail the disadvantage that in view of the very high pressures under the influence of the compression of the first-mentioned piston, a liquefaction process of the gas in the housing region occurs. Accordingly, however, can be alternatively or additionally by using a compression spring as a spring memory, the system pressures safely dominate.
  • FIGURE shows in longitudinal section the device according to the invention for damping pressure surges with two different embodiments of cover parts.
  • the device shown in the figure is used to dampen pressure surges in a fluid, in particular in the form of diesel fuel, wherein the device has a cylindrical housing 10. Furthermore, the device has a against the biasing force of a spring accumulator 12 in the housing 10 longitudinally movable piston 14.
  • the pertinent piston 14 is formed in the manner of a cylindrical contact plate and along its outer periphery via a sliding and / or sealing ring 16 along the cylindrical Inner circumference 18 of the housing 10 out.
  • the piston 14 accordingly has on its opposite sides two substantially planar abutment surfaces 20,22 and the end-side guide of the spring accumulator 12, the piston 14 is provided on its side facing thereto with a cylindrical guide surface 22, the outer circumference also on the inner circumference 18 of Housing 10 is supported.
  • the piston 14 cooperates with a further piston 24, wherein the further piston 24 is guided in a connecting piece 26 of the housing 10 so as to be longitudinally movable. Further, as the illustration of the figure shows, the piston 14 acts in the housing with a compressive force on the further piston 24 in each operating travel position, also in its shown foremost end stop position during operation or use of the device.
  • the fitting 26 tapers towards the free end of the housing 10 and is provided on the outer peripheral side with a connecting thread 28, with which the housing 10 can be connected in the arrangement shown to a fluid system, for example to the diesel supply line for an injector system according to the common -Rail technology.
  • the housing 10 is located in a connecting line, which leads to a hydraulic pump, in particular positive displacement pump, for example in the form of a diesel fuel pump or the like.
  • a hydraulic pump in particular positive displacement pump, for example in the form of a diesel fuel pump or the like.
  • the pressure surges created during operation of the diesel fuel pump which can be considerable at system pressures of up to 2200 bar and more, are to be damped and smoothed with the device according to the invention, with high-frequency fluid pulses also being compensated.
  • the damping device according to the invention should be effective even at very high pressure amplitudes independently thereof in predeterminable limits.
  • Said connecting piece 26 merges into a length-reinforced base 30 of the housing 10 and said pistons 14, 24 and the spring accumulator 12 are oriented in their longitudinal direction on the longitudinal axis 32 of the housing 10 and connecting piece 26. Further, the piston 14 in diameter by a multiple larger than the diameter of the further piston 24, so that in view of the change in the diameter ratio, a very good impact force is introduced between further piston 24 and the first piston sixteenth
  • the further piston 24 is thus formed in the manner of a punch or plunger and guided over at least one captive 34 in the form of a locking ring in the through-housing opening 36 of the connecting piece 26.
  • the captive 34 may consist in particular of a retaining ring which closes the housing opening 36 to the outside at the front end and abuts the front end of the further piston 24 in its front boundary position at the supernatant thereof.
  • the length of the further piston 24 is dimensioned such that it maintains an axial distance from the captive 34 with a small clearance.
  • the piston 14 then exerts a pressure force on it in each displacement position of the further piston 24.
  • the further piston 24 on the outer circumference side is so finely worked, in particular lapped, that a metallically tight gap 38 is achieved at least between parts of the outer periphery of the further piston 24 and the inner wall of the housing opening 36.
  • the further piston 24 on the outer peripheral side ring or lubrication grooves 40 Such a labyrinth seal is achieved, which makes it more difficult for the diesel fuel the housing opening 36 into the space 42 within the housing 10 between the contact surface 20 and the bottom surface 44 facing the bottom 30 to penetrate.
  • a sealing system 48 is provided in the front, frontal region of the bottom 30, for example in the form of a conventional ring seal.
  • a compression spring in the form of a coil spring wherein the housing interior may also be additionally acted upon by a pressurized gas, for example in the form of a nitrogen gas.
  • the pertinent compression spring 12 extends between the piston 14 and a cover part 50, wherein the cover part 50 may be formed from a holding plate 52 which is held in the housing 10 via a securing means, in particular a securing ring 54.
  • a cover part 50 consists of a screw 56, the outer peripheral side via an external thread 58 of the housing 10 can be screwed onto this.
  • the device according to the invention it is ensured that any occurring leakage flows are safely controlled and due to the separate piston arrangement of the pistons 14 and 24 it is ensured that there is no tilting.
  • very high-frequency pressure surges acting on the punch-like further piston 24 can be in the same frequency impulsively pass on to the piston 16, which under the influence of the spring accumulator 12 and in response to the other piston 24 then performs the pulsation damping or Pulsationsglättung .
  • the system shown can be realized in particular on the housing side 10 of conventional steel materials in a cost effective manner and manufacturing technology.
  • the device according to the invention can generally be used where low volumes have to be level-regulated or displaced at high pressure. Due to the area ratios of the piston, the spring to be used can build smaller, since the required force is reduced accordingly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
EP04790081A 2003-10-31 2004-10-01 Vorrichtung zum dämpfen von druckstössen Expired - Lifetime EP1685323B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10350941A DE10350941A1 (de) 2003-10-31 2003-10-31 Vorrichtung zum Dämpfen von Druckstößen
PCT/EP2004/010971 WO2005052348A1 (de) 2003-10-31 2004-10-01 Vorrichtung zum dämpfen von druckstössen

Publications (2)

Publication Number Publication Date
EP1685323A1 EP1685323A1 (de) 2006-08-02
EP1685323B1 true EP1685323B1 (de) 2010-06-23

Family

ID=34529988

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04790081A Expired - Lifetime EP1685323B1 (de) 2003-10-31 2004-10-01 Vorrichtung zum dämpfen von druckstössen

Country Status (6)

Country Link
US (1) US7308910B2 (enrdf_load_stackoverflow)
EP (1) EP1685323B1 (enrdf_load_stackoverflow)
JP (1) JP2007511695A (enrdf_load_stackoverflow)
AT (1) ATE472053T1 (enrdf_load_stackoverflow)
DE (2) DE10350941A1 (enrdf_load_stackoverflow)
WO (1) WO2005052348A1 (enrdf_load_stackoverflow)

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
FI120214B (fi) * 2005-12-22 2009-07-31 Waertsilae Finland Oy Järjestely mäntämoottorin polttoaineen syöttöjärjestelmän paineen värähtelyn vaimentamiseksi
US20090191068A1 (en) * 2008-01-29 2009-07-30 Clark Equipment Company Variable volume reservoir
MX2011011032A (es) * 2009-04-20 2012-01-20 Dgc Ind Pty Ltd Un sistema de suministro dual para un sistema de inyeccion indirecta de un motor diesel.
DE102009032212A1 (de) * 2009-07-03 2011-01-05 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Hydraulischer Schwenkmotor
US8387665B2 (en) * 2009-12-10 2013-03-05 GM Global Technology Operations LLC Combination spring and gas filled accumulator
US8464742B2 (en) * 2010-02-11 2013-06-18 Honeywell International Inc. Injection or other system with anti-thermal lockdown mechanism and related method
DE102010064169A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Druckspeichervorrichtung für ein Kraftstoffeinspritzsystem
US8794108B2 (en) * 2011-06-13 2014-08-05 Sonnax Industries, Inc. Automatic transmission fluid accumulator replacement assembly
US8656959B2 (en) * 2011-09-23 2014-02-25 GM Global Technology Operations LLC Hydraulic accumulator
US9677519B2 (en) * 2013-08-27 2017-06-13 Kia Motors Corporation Device for decreasing fuel pulsation of LPG vehicle
CN110939614B (zh) * 2019-12-14 2021-06-25 哈尔滨工业大学 宽频带弹簧振子液压脉动衰减器

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Also Published As

Publication number Publication date
ATE472053T1 (de) 2010-07-15
WO2005052348A1 (de) 2005-06-09
JP2007511695A (ja) 2007-05-10
DE10350941A1 (de) 2005-06-02
US7308910B2 (en) 2007-12-18
DE502004011318D1 (enrdf_load_stackoverflow) 2010-08-05
EP1685323A1 (de) 2006-08-02
US20060225800A1 (en) 2006-10-12

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