EP1685323A1 - Device for damping pressure surges - Google Patents

Device for damping pressure surges

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Publication number
EP1685323A1
EP1685323A1 EP04790081A EP04790081A EP1685323A1 EP 1685323 A1 EP1685323 A1 EP 1685323A1 EP 04790081 A EP04790081 A EP 04790081A EP 04790081 A EP04790081 A EP 04790081A EP 1685323 A1 EP1685323 A1 EP 1685323A1
Authority
EP
European Patent Office
Prior art keywords
piston
housing
spring
fluid
guided
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
EP04790081A
Other languages
German (de)
French (fr)
Other versions
EP1685323B1 (en
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/en
Application granted granted Critical
Publication of EP1685323B1 publication Critical patent/EP1685323B1/en
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 piston which can be moved slowly in the housing against the prestressing force of a spring accumulator.
  • the devices in question include the so-called hydraulic accumulators, one of the main tasks of hydraulic accumulators being to absorb certain volumes of pressurized liquid in a hydraulic system and to return these to the system if necessary. Since the liquid is under pressure, the hydraulic accumulators are treated like pressure vessels and must be designed for the maximum operating pressure, taking into account the acceptance standards.
  • the hydraulic fluid in the hydraulic accumulator is loaded by weight or spring or charged with gas. There is always a balance between the pressure of the hydraulic fluid and the back pressure generated by the weight of the spring or the gas.
  • hydro-pneumatic, ie gas-loaded accumulators with a separating element are used, whereby a distinction is made between bladder, piston and membrane accumulators depending on the design of the separating element.
  • the hydropneumatic accumulators mentioned have to perform a wide variety of tasks in a hydraulic system and, for example, in addition to the energy storage mentioned, they can also be used for damping mechanical shocks and for damping pressure surges in the hydraulic system.
  • hydraulic pumps such as positive displacement pumps
  • pulsations occur in the volume flow, these pulsations not only causing noise but also vibrations, which can damage the entire hydraulic system.
  • the aforementioned hydraulic pumps in particular displacement pumps, are also used in what is known as common rail technology in the field of diesel engines.
  • Newer developments of the third generation rely on piezo technology for the injection systems for the diesel fuel.
  • the newly developed piezo inline injectors for the third generation of common parts (cf. VDI - News No. 33 dated August 15, 2003) use piezo actuator modules, which are connected to switching valves via coupler modules and to a fuel nozzle module -Injection system, whereby the outstanding hydraulic speed of the system results from the high degree of integration of the inline injector, ie from the proximity of the piezo package to the nozzle needle in the tip of the injector.
  • the moving mass of the new systems was reduced from 16g to 4g, whereby moving mass is understood to mean the mass of the nozzle needle and the fuel that fills the control room.
  • Very high system pressures are required for this technical design, which can reach up to 2200 bar.
  • the system pressure in question is to be built up by the hydraulic pump mentioned, in particular a positive displacement pump, with the described disadvantage of the pressure and pulsation surges that occur. If the pressure surges are passed on to the injector system, this can lead to critical see system states and lead to a failure of the piezo injector system and the injection system. Insofar as what is known (cf.
  • DE 101 48 220 A1 discloses a further device for damping pressure pulsations in a fluid system, in particular in a fuel system of an internal combustion engine, the known device comprising a housing in which at least one working space is present. This is connected to the fluid system and is delimited in some areas by at least one movable wall element in the form of a metal membrane, which is fixed stationary on the edge side in the housing. This wall element is operatively connected to a first spring device and in order to be able to smooth out pressure pulsations even at variable pressure in the fluid system, it is provided that the device comprises at least one second movable wall element which delimits a second working space and likewise from a metal membrane fixed in the edge of the housing consists. The first spring device is between the two
  • Wall elements arranged in the form of the membranes and operatively connected to both. Furthermore, a throttle device is provided, via which the second working space is connected to the fluid system.
  • the invention has for its object to provide a device for damping pressure surges, with which it is possible, even at very high system pressures up to 2200 bar occurring pressure surges, caused by a hydraulic pump, especially diesel fuel pump, damping and / or smoothing such that no harmful force is introduced into a piezo injector system of common rail technology.
  • a relevant object is achieved by a device with the features of claim 1 in its entirety.
  • the piston cooperates with a further piston which is guided so that it can move slowly in a connecting piece of the housing, and that when the device operates, the piston exerts a compressive force on the further piston in each travel position thereof Master very high-frequency pressure surges in the diesel fuel system in a functionally reliable manner, even if very high system pressures of up to 2200 bar and more are generated due to the hydraulic pump in the form of the diesel fuel pump.
  • the mechanical decoupling of the two pistons mentioned and the permanent introduction of pressure from one piston to the other piston ensures that the pressure surges that are introduced can be safely absorbed and controlled, and in particular the decoupling of the pistons ensures that any leaks with accompanying leakage flows are kept to a minimum are or are controlled in such a way that functional failures in the overall system are avoided.
  • the diameter of one piston is several times larger than the diameter of the other piston, and it has been shown that the arrangement in question enables an unrestricted actuation process to be achieved with the pistons.
  • Special tilting operations of the other piston in the connector of the housing are avoided in this way by its separate, independent guidance.
  • the further piston is designed in the manner of a stamp and is guided in at least one captive device in a continuous housing opening in the connecting piece. In this way, the respective pistons can be moved freely between predeterminable travel barriers in the housing arrangement.
  • the further piston is finely machined, in particular lapped, on the outer circumference side, in such a way that a metallic tight gap is achieved at least between parts of the outer circumference and the further piston on the inner wall of the housing opening.
  • the additional piston can be provided on the outer circumference with ring or lubrication grooves. In this way, despite the high pressures of up to 2200 bar and more in the diesel fluid system, the additional piston is reliably sealed from the interior of the housing with the first piston, and in particular when using the ring or lubrication grooves on the outer circumference of the additional piston, a fluid seal can be created build up that counteracts the fluid entry into the metallic gap.
  • a leakage opening arranged in the housing opens into the fluid space between the pistons, the diesel fluid which nevertheless penetrates into the housing interior can be made in the manner of a return bore for leakage oil. dium are released without pressure in the block towards the tank or leak side.
  • the device according to the invention is explained in more detail using an exemplary embodiment according to the drawing.
  • the single figure shows in longitudinal section the device according to the invention for damping pressure surges with two different embodiments on cover parts.
  • the device shown in the figure serves to dampen pressure surges in a fluid, in particular in the form of diesel fuel, the device having a cylindrical housing 10. Furthermore, the device has a piston 14 which can be moved slowly in the housing 10 against the prestressing force of a spring accumulator 12.
  • the piston 14 in question is designed in the manner of a cylindrical contact plate and along its outer circumference via a sliding and / or sealing ring 16 along the cylindrical see inner circumference 18 of the housing 10 out.
  • the piston 14 accordingly has on its opposite sides two substantially flat contact surfaces 20, 22 and for guiding the spring 12 at the end, the piston 14 is provided on its side with a cylindrical guide surface 22, which is also on the outer circumference on the inner circumference 18 of the Housing 10 supports.
  • the piston 14 cooperates with a further piston 24, the further piston 24 in this regard being guided so that it can move slowly in a connecting piece 26 of the housing 10. Furthermore, as the illustration according to the figure shows, the piston 14 acts on the further piston 24 in the housing with a compressive force in every operating travel position, also in its foremost end stop position shown during operation or use of the device.
  • the connector 26 tapers towards the free end of the housing 10 and is provided on the outer circumference with a connection 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 a positive displacement pump, for example in the form of a diesel fuel pump or the like.
  • a hydraulic pump in particular a positive displacement pump, for example in the form of a diesel fuel pump or the like.
  • the pressure surges that occur 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 using the device according to the invention, wherein high-frequency fluid surges are also to be compensated for.
  • the damping device according to the invention is intended to be effective, even at very high pressure amplitudes, in predefinable limit ranges.
  • Said connecting piece 26 merges into a lengthened bottom 30 of the housing 10 and the pistons 14, 24 and the spring accumulator 12 are oriented in their longitudinal orientation on the longitudinal axis 32 of the housing 10 and connecting piece 26. ben 14 in diameter several times larger than the diameter of the further piston 24, so that, with regard to the change in the diameter ratio, very good impact force is introduced between the further piston 24 and the first piston 16.
  • the further piston 24 is thus designed in the manner of a plunger or plunger and is guided in the continuous housing opening 36 of the connecting piece 26 via at least one captive lock 34 in the form of a securing ring.
  • the captive device 34 can in particular consist of a retaining ring which closes the housing opening 36 to the outside at the front end and on the projection of which the front end of the further piston 24 abuts in its front limiting position.
  • the length of the further piston 24 is dimensioned such that it maintains an axial distance from the captive device 34 with a small amount of play.
  • the piston 14 then exerts a compressive force on the additional piston 24 in each travel position.
  • the additional piston 24 is finely machined, in particular lapped, on the outer circumferential side in such a way that a metal-tight gap 38 is achieved at least between parts of the outer circumference of the additional piston 24 and the inner wall of the housing opening 36.
  • the additional piston 24 has ring or lubrication grooves 40 on the outer circumferential side. In this way, a labyrinth seal is achieved, which makes it more difficult for the diesel fuel penetrate the housing opening 36 into the space 42 within the housing 10 between the contact surface 20 and the bottom surface 44 of the bottom 30 facing it.
  • a leakage opening 46 arranged in the housing 10 in the manner of a bore opens into the fluid or intermediate space 42 between the pistons 14, 24 and a deliberately provided gap or leakage stream can flow through the sealing system in the form of the ring or lubrication grooves 40 Metallic gap 38 and the space 42 are discharged through the leakage opening 46 to the unpressurized leak or tank side of the overall system.
  • a sealing system 48 is provided in the front, front area of the base 30, for example in the form of a conventional ring seal.
  • a compression spring in the form of a helical spring serves as the spring accumulator 12, and the interior of the housing can also be acted upon with a compressed gas, for example in the form of a nitrogen gas.
  • the relevant compression spring 12 extends between the piston 14 and a cover part 50, the cover part 50 being able to be formed from a holding plate 52 which is held in the housing 10 by means of a securing means, in particular a securing ring 54.
  • An alternative embodiment is shown in the figure in a square frame and in this case the cover part 50 consists of a screw cover 56 which can be screwed onto the outer circumference via an external thread 58 of the housing 10.
  • the device according to the invention it is ensured that any leakage flows that occur are safely controlled and the separate piston arrangement of the pistons 14 and 24 ensures that canting does not occur.
  • very high-frequency pressure surges which act on the piston-like further piston 24, can be passed on to the piston 16 at the same frequency, which then under the influence of the spring accumulator 12 and with the effect on the further piston 24, the pulsation damping or pulsation ons smoothing.
  • the system shown can be implemented, in particular, on the housing side 10 from conventional steel materials in a cost-effective manner and is easy to manufacture.
  • the device according to the invention can generally be used where small volumes have to be level-damped or shifted at high pressure. Due to the area ratio of the pistons, the spring to be used can be 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)

Abstract

A device for damping pressure surges in a fluid with a housing ( 10 ) and a piston ( 14 ) that can be longitudinally displaced inside the housing ( 10 ) against the pretensioning force of a spring energy store ( 12 ). The piston ( 14 ) interacts with another piston ( 24 ), which is guided in a connecting piece ( 26 ) of the housing ( 10 ) in a manner that enables it to be longitudinally displaced. During the operation of the device, the piston ( 14 ) exerts a pressure force onto the other piston ( 24 ) when the other piston is in any displacement position. Even pressure surges occurring with a high frequency can be reliably controlled in a functionally reliable manner.

Description

Hydac Technology GmbH, Industriegebiet, 66280 Sulzbach/Saar Hydac Technology GmbH, industrial area, 66280 Sulzbach / Saar
Vorrichtung zum Dämpfen von DruckstößenDevice for damping pressure surges
Die Erfindung betrifft eine Vorrichtung zum Dämpfen von Druckstößen in einem Fluid mit einem Gehäuse und einem gegen die Vorspannkraft eines Federspeichers in dem Gehäuse langsverfahrbaren Kolben.The invention relates to a device for damping pressure surges in a fluid with a housing and a piston which can be moved slowly in the housing against the prestressing force of a spring accumulator.
Zu den dahingehenden Vorrichtungen zählen die sog. Hydrospeicher, wobei eine der Hauptaufgaben von Hydrospeichern es ist, bestimmte Volumen unter Druck stehender Flüssigkeit einer Hydroanlage aufzunehmen und diese bei Bedarf wieder an die Anlage zurück zu geben. Da sich die Flüssigkeit unter Druck befindet, werden die Hydrospeicher wie Druckbehälter behandelt und müssen für den maximalen Betriebsüberdruck unter Berücksichtigung der Abnahmestandards ausgelegt sein. Zum Volumenausgleich im Hydrospeicher und der damit verbundenen Energiespeicherung wird die Druckflüssigkeit im Hydrospeicher gewichts- oder federbelastet oder mit Gas beaufschlagt. Dabei herrscht zwischen dem Druck der Druckflüssigkeit und dem vom Gewicht der Feder oder dem vom Gas erzeugten Gegendruck stets ein Gleichgewicht. In den meisten Hydroanlagen werden hy- dropneumatische, also gasbeaufschlagte Speicher mit Trennelement eingesetzt, wobei man je nach Ausbildung des Trennelementes unterscheidet zwischen Blasen-, Kolben- und Membranspeichem. Die genannten hydropneumatischen Speicher haben in einer Hydroanlage verschiedenste Aufgaben zu erfüllen und können beispielsweise neben der genannten Energiespeicherung auch zur Dämpfung mechanischer Stöße sowie zur Druckstoßdämpfung im hydraulischen System mit beigezogen werden. Insbesondere bei Einsatz von hydraulischen Pumpen, wie Verdrängerpumpen, entstehen Pulsationen im Volumenstrom, wobei diese Pulsationen neben Lärm auch Vibrationen verursachen, was zu einer Schädigung der gesamten Hydroanlage führen kann.The devices in question include the so-called hydraulic accumulators, one of the main tasks of hydraulic accumulators being to absorb certain volumes of pressurized liquid in a hydraulic system and to return these to the system if necessary. Since the liquid is under pressure, the hydraulic accumulators are treated like pressure vessels and must be designed for the maximum operating pressure, taking into account the acceptance standards. In order to balance the volume in the hydraulic accumulator and the associated energy storage, the hydraulic fluid in the hydraulic accumulator is loaded by weight or spring or charged with gas. There is always a balance between the pressure of the hydraulic fluid and the back pressure generated by the weight of the spring or the gas. In most hydraulic systems, hydro-pneumatic, ie gas-loaded accumulators with a separating element are used, whereby a distinction is made between bladder, piston and membrane accumulators depending on the design of the separating element. The hydropneumatic accumulators mentioned have to perform a wide variety of tasks in a hydraulic system and, for example, in addition to the energy storage mentioned, they can also be used for damping mechanical shocks and for damping pressure surges in the hydraulic system. In particular when using hydraulic pumps, such as positive displacement pumps, pulsations occur in the volume flow, these pulsations not only causing noise but also vibrations, which can damage the entire hydraulic system.
Die genannten Hydro-, insbesondere Verdrängerpumpen finden auch Anwendung in der sog. Common-Rail-Technik im Bereich von Dieselmotoren. Neuere Entwicklungen der dritten Generation setzen dabei für die Einspritzsysteme für den Dieselkraftstoff auf die Piezotechnik. Die dabei neu entwickelten Piezo-Inline-Injektoren für die dritte Common- ail-Generation (vgl. VDI - Nachrichten Nr. 33 vom 15. August 2003) verwenden Piezo- Aktormodule, die über Kopplermodule auf Schaltventile und diese wiederum auf ein Düsenmodul des Kraftstoff-Einspritzsystems einwirken, wobei sich die herausragende hydraulische Schnelligkeit des Systems aus dem hohen Integrationsgrad des Inline-Injektors ergibt, d.h. aus der Nähe des Piezo-Paketes zur Düsennadel in der Spitze des Injektors. Im Vergleich zur vorangegangenen Generation wurde dabei bei den neuen Systemen die bewegte Masse von 16g auf 4g reduziert, wobei man unter bewegter Masse die Masse der Düsennadel und des Kraftstoffes versteht, der den Steuerraum füllt. Für die dahingehende technische Auslegung sind sehr hohe System- drücke notwendig, die bis in die Größenordnung von 2200 bar heranreichen. Der dahingehende Systemdruck ist von der genannten Hydropumpe, insbesondere Verdrängerpumpe, aufzubauen mit dem beschriebenen Nachteil der auftretenden Druck- und Pulsationsstöße. Werden die dahingehenden Druckstöße an das Injektorsystem weitergegeben, kann dies zu kriti- sehen Systemzuständen führen und zu einem Ausfall der Piezo-Injektor- anlage nebst Einspritzsystem. Sofern man, was bekannt ist (vgl. DE 195 39 885 A1), im oben skizzierten Sinne übliche Hydrospeicher mit Trennelement (Kolben) zur Pulsations- und Druckstoßdämpfung in das Diesel- Fluidsystem mit einbezieht, finden diese jedoch regelmäßig ihre Grenzen im Hinblick auf die genannten hohen Systemdrücke bis 2200 bar.The aforementioned hydraulic pumps, in particular displacement pumps, are also used in what is known as common rail technology in the field of diesel engines. Newer developments of the third generation rely on piezo technology for the injection systems for the diesel fuel. The newly developed piezo inline injectors for the third generation of common parts (cf. VDI - News No. 33 dated August 15, 2003) use piezo actuator modules, which are connected to switching valves via coupler modules and to a fuel nozzle module -Injection system, whereby the outstanding hydraulic speed of the system results from the high degree of integration of the inline injector, ie from the proximity of the piezo package to the nozzle needle in the tip of the injector. Compared to the previous generation, the moving mass of the new systems was reduced from 16g to 4g, whereby moving mass is understood to mean the mass of the nozzle needle and the fuel that fills the control room. Very high system pressures are required for this technical design, which can reach up to 2200 bar. The system pressure in question is to be built up by the hydraulic pump mentioned, in particular a positive displacement pump, with the described disadvantage of the pressure and pulsation surges that occur. If the pressure surges are passed on to the injector system, this can lead to critical see system states and lead to a failure of the piezo injector system and the injection system. Insofar as what is known (cf. DE 195 39 885 A1) includes, in the sense outlined above, conventional hydraulic accumulators with a separating element (piston) for damping pulsations and pressure surges in the diesel fluid system, these regularly find their limits with regard to the mentioned high system pressures up to 2200 bar.
Durch die DE 101 48 220 A1 ist eine weitere Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem bekannt, insbesondere in ei- nem Kraftstoffsystem einer Brennkraftmaschine, wobei die bekannte Vorrichtung ein Gehäuse umfaßt, in dem mindestens ein Arbeitsraum vorhanden ist. Dieser ist mit dem Fluidsystem verbunden und wird bereichsweise von mindestens einem beweglichen Wandelement in Form einer Metallmembran begrenzt, die randseitig im Gehäuse stationär festgelegt ist. Dieses Wandelement ist mit einer ersten Federeinrichtung wirkverbunden und um Druckpulsationen auch bei variablem Druck im Fluidsystem glätten zu können, ist vorgesehen, dass die Vorrichtung mindestens ein zweites bewegliches Wandelement umfaßt, welches einen zweiten Arbeitsraum begrenzt und gleichfalls aus einer randseitig im Gehäuse festgelegen Metall- membran besteht. Die erste Federeinrichtung ist zwischen den beidenDE 101 48 220 A1 discloses a further device for damping pressure pulsations in a fluid system, in particular in a fuel system of an internal combustion engine, the known device comprising a housing in which at least one working space is present. This is connected to the fluid system and is delimited in some areas by at least one movable wall element in the form of a metal membrane, which is fixed stationary on the edge side in the housing. This wall element is operatively connected to a first spring device and in order to be able to smooth out pressure pulsations even at variable pressure in the fluid system, it is provided that the device comprises at least one second movable wall element which delimits a second working space and likewise from a metal membrane fixed in the edge of the housing consists. The first spring device is between the two
Wandelementen in Form der Membranen angeordnet und mit beiden wirkverbunden. Ferner ist eine Drosseleinrichtung vorgesehen, über welche der zweite Arbeitsraum mit dem Fluidsystem verbunden ist. Mit der bekannten Lösung lassen sich zwar Druckpulsationen in einem Fluidsystem bei unter- schiediichen Druckniveaus zuverlässig und gut glätten. Aufgrund der festen Einspannung der Wandelemente (Membrane) ist aber deren Bewegbarkeit eingeschränkt, so dass bei hohen Drücken und entsprechend großen Pulsations- und Druckstößen ein funktionssicherer Betrieb gefährdet sein kann. Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine Vorrichtung zum Dämpfen von Druckstößen zur Verfügung zu stellen, mit der es möglich ist, auch bei sehr hohen Systemdrücken bis 2200 bar auftretende Druckstöße, hervorgerufen durch eine Hydropumpe, insbesondere Dieselkraftstoff pumpe, derart zu dämpfen und/oder zu glätten, dass keine schädlichen Krafteinleitungen in ein Piezo-Injektorsystem der Common-Rail-Technik erfolgt. Eine dahingehende Aufgabe löst eine Vorrichtung mit den Merkmalen des Patentanspruches 1 in seiner Gesamtheit.Wall elements arranged in the form of the membranes and operatively connected to both. Furthermore, a throttle device is provided, via which the second working space is connected to the fluid system. With the known solution, pressure pulsations in a fluid system can be smoothed reliably and well at different pressure levels. Due to the firm clamping of the wall elements (membrane), their mobility is restricted, so that reliable operation can be jeopardized at high pressures and correspondingly large pulsation and pressure surges. Based on this prior art, the invention has for its object to provide a device for damping pressure surges, with which it is possible, even at very high system pressures up to 2200 bar occurring pressure surges, caused by a hydraulic pump, especially diesel fuel pump, damping and / or smoothing such that no harmful force is introduced into a piezo injector system of common rail technology. A relevant object is achieved by a device with the features of claim 1 in its entirety.
Dadurch, dass gemäß dem kennzeichnenden Teil des Patentanspruches 1 der Kolben mit einem weiteren Kolben zusammenwirkt, der in einem Anschlußstück des Gehäuses langsverfahrbar geführt ist, und dass beim Betrieb der Vorrichtung der Kolben in jeder Verfahrstellung des weiteren Kolbens auf diesen eine Druckkraft ausübt, lassen sich in funktionssicherer Weise auch sehr hochfrequente Druckstöße im Dieselkraftstoffsystem sicher beherrschen, auch wenn bedingt durch die Hydropumpe in Form der Dieselkraftstoffpumpe sehr hohe Systemdrücke von bis zu 2200 bar und mehr erzeugt sind. Durch die mechanische Entkopplung der beiden genannten Kolben und die permanente Druckkrafteinleitung des einen Kolbens auf den weiteren Kolben ist sichergestellt, dass die eingeleiteten Druckstöße sicher aufgefangen und beherrscht werden können und insbesondere ist durch die Entkopplung der Kolben sichergestellt, dass etwaige Undichtigkeiten mit einhergehenden Leckageströmen gering gehalten sind oder derge- stalt beherrscht werden, dass Funktionsausfälle im Gesamtsystem vermieden sind. Vorzugsweise ist dabei vorgesehen, dass der eine Kolben im Durchmesser um ein Mehrfaches größer ist als der Durchmesser des weiteren Kolbens und es hat sich gezeigt, dass durch die dahingehende Anordnung ein hemmfreier Ansteuervorgang mit den Kolben erreichbar ist. Insbe- sondere Verkantungsvorgänge des weiteren Kolbens im Anschlußstück des Gehäuses sind durch seine getrennte, eigenständige Führung derart vermieden.Characterized in that, according to the characterizing part of claim 1, the piston cooperates with a further piston which is guided so that it can move slowly in a connecting piece of the housing, and that when the device operates, the piston exerts a compressive force on the further piston in each travel position thereof Master very high-frequency pressure surges in the diesel fuel system in a functionally reliable manner, even if very high system pressures of up to 2200 bar and more are generated due to the hydraulic pump in the form of the diesel fuel pump. The mechanical decoupling of the two pistons mentioned and the permanent introduction of pressure from one piston to the other piston ensures that the pressure surges that are introduced can be safely absorbed and controlled, and in particular the decoupling of the pistons ensures that any leaks with accompanying leakage flows are kept to a minimum are or are controlled in such a way that functional failures in the overall system are avoided. It is preferably provided that the diameter of one piston is several times larger than the diameter of the other piston, and it has been shown that the arrangement in question enables an unrestricted actuation process to be achieved with the pistons. In particular, Special tilting operations of the other piston in the connector of the housing are avoided in this way by its separate, independent guidance.
Bei einer bevorzugten Ausführungsform der erfindungsgemäßen Vorrichtung ist der weitere Kolben in der Art eines Stempels ausgebildet und über mindestens eine Verliersicherung in einer durchgehenden Gehäuseöffnung des Anschlußstückes geführt. Auf diese Art und Weise ist die freie Verfahr- barkeit der jeweiligen Kolben zwischen vorgebbaren Verfahrschranken in der Gehäuseanordnung erreicht.In a preferred embodiment of the device according to the invention, the further piston is designed in the manner of a stamp and is guided in at least one captive device in a continuous housing opening in the connecting piece. In this way, the respective pistons can be moved freely between predeterminable travel barriers in the housing arrangement.
Bei einer weiteren bevorzugten Ausführungsform der erfindungsgemäßen Vorrichtung ist der weitere Kolben außenumfangsseitig derart feinstbearbei- tet, insbesondere geläppt, dass ein metallisch dichter Spalt zumindest zwi- sehen Teilen des Außenumfanges und des weiteren Kolbens an der Innenwandung der Gehäuseöffnung erreicht ist. In weiterer Ausgestaltung des genannten Dichtsystems kann der weitere Kolben außenumfangsseitig mit Ring- oder Schmiernuten versehen sein. Hierdurch wird trotz der hohen Drücke von bis zu 2200 bar und mehr im Diesel-Fluidsystem eine sichere Abdichtung des weiteren Kolbens gegenüber dem Gehäuseinneren mit dem ersten Kolben erreicht und insbesondere bei Einsatz der Ring- oder Schmiernuten am Außenumfang des weiteren Kolbens kann sich dergestalt eine Fluiddichtung aufbauen, die dem Fluideintritt in den metallischen Spalt entgegenwirkt.In a further preferred embodiment of the device according to the invention, the further piston is finely machined, in particular lapped, on the outer circumference side, in such a way that a metallic tight gap is achieved at least between parts of the outer circumference and the further piston on the inner wall of the housing opening. In a further embodiment of the sealing system mentioned, the additional piston can be provided on the outer circumference with ring or lubrication grooves. In this way, despite the high pressures of up to 2200 bar and more in the diesel fluid system, the additional piston is reliably sealed from the interior of the housing with the first piston, and in particular when using the ring or lubrication grooves on the outer circumference of the additional piston, a fluid seal can be created build up that counteracts the fluid entry into the metallic gap.
Sofern bei einer bevorzugten Ausführungsform der erfindungsgemäßen Vorrichtung in den Fluidraum zwischen den Kolben eine im Gehäuse angeordnete Leckageöffnung mündet, kann dergestalt in der Art einer Rücklaufbohrung für Lecköl das dennoch in das Gehäuseinnere eindringende Dieselme- dium drucklos im Block in Richtung auf die Tank- oder Leckageseite abgegeben werden.If, in a preferred embodiment of the device according to the invention, a leakage opening arranged in the housing opens into the fluid space between the pistons, the diesel fluid which nevertheless penetrates into the housing interior can be made in the manner of a return bore for leakage oil. dium are released without pressure in the block towards the tank or leak side.
Im Hinblick auf die angesprochenen sehr hohen Drücke hat es sich als vor- teilhaft erwiesen, als Federspeicher mindestens eine als Druckfeder ausgebildete Schraubenfeder und/oder ein Druckgas vorzusehen. Der Einsatz eines reinen Druckgases bringt gegebenenfalls den Nachteil mit sich, dass im Hinblick auf die sehr hohen Drücke es unter dem Einfluß der Kompression des erstgenannten Kolbens zu einem Verflüssigungsvorgang des Gases in dem Gehäusebereich kommt. Demgemäß lassen sich aber alternativ oder zusätzlich durch Einsatz einer Druckfeder als Federspeicher die genannten Systemdrücke sicher beherrschen.In view of the very high pressures mentioned, it has proven to be advantageous to provide at least one helical spring designed as a compression spring and / or a compressed gas as the spring accumulator. The use of a pure compressed gas may have the disadvantage that, in view of the very high pressures, the gas in the housing area is liquefied under the influence of the compression of the first-mentioned piston. Accordingly, as an alternative or in addition, the use of a compression spring as the spring accumulator can safely control the system pressures mentioned.
Weitere vorteilhafte Ausführungsformen der erfindungsgemäßen Vorrich- tung sind Gegenstand der sonstigen Unteransprüche.Further advantageous embodiments of the device according to the invention are the subject of the other subclaims.
Im folgenden wird die erfindungsgemäße Vorrichtung anhand eines Ausführungsbeispiels nach der Zeichnung näher erläutert. Dabei zeigt in prinzipieller und nicht maßstäblicher Darstellung die einzige Figur im Längsschnitt die erfindungsgemäße Vorrichtung zum Dämpfen von Druckstößen mit zwei verschiedenen Ausführungsformen an Deckelteilen.In the following, the device according to the invention is explained in more detail using an exemplary embodiment according to the drawing. In principle and not to scale, the single figure shows in longitudinal section the device according to the invention for damping pressure surges with two different embodiments on cover parts.
Die in der Figur gezeigte Vorrichtung dient dem Dämpfen von Druckstößen in einem Fluid, insbesondere in Form von Dieselkraftstoff, wobei die Vor- richtung ein zylindrisches Gehäuse 10 aufweist. Ferner weist die Vorrichtung einen gegen die Vorspannkraft eines Federspeichers 12 in dem Gehäuse 10 langsverfahrbaren Kolben 14 auf. Der dahingehende Kolben 14 ist in der Art einer zylindrischen Anlageplatte ausgebildet und entlang seines Außenumfanges über einen Gleit- und/oder Dichtring 16 längs des zylindri- sehen Innenumfanges 18 des Gehäuses 10 geführt. Der Kolben 14 weist demgemäß an seinen einander gegenüberliegenden Seiten zwei im wesentlichen plane Anlageflächen 20,22 auf und zur endseitigen Führung des Federspeichers 12 ist der Kolben 14 an seiner dahingehend gerichteten Seite mit einer zylindrischen Führungsfläche 22 versehen, die sich außenumfangsseitig gleichfalls am Innenumfang 18 des Gehäuses 10 abstützt.The device shown in the figure serves to dampen pressure surges in a fluid, in particular in the form of diesel fuel, the device having a cylindrical housing 10. Furthermore, the device has a piston 14 which can be moved slowly in the housing 10 against the prestressing force of a spring accumulator 12. The piston 14 in question is designed in the manner of a cylindrical contact plate and along its outer circumference via a sliding and / or sealing ring 16 along the cylindrical see inner circumference 18 of the housing 10 out. The piston 14 accordingly has on its opposite sides two substantially flat contact surfaces 20, 22 and for guiding the spring 12 at the end, the piston 14 is provided on its side with a cylindrical guide surface 22, which is also on the outer circumference on the inner circumference 18 of the Housing 10 supports.
Der Kolben 14 wirkt mit einem weiteren Kolben 24 zusammen, wobei der dahingehend weitere Kolben 24 in einem Anschlußstück 26 des Gehäuses 10 langsverfahrbar geführt ist. Ferner wirkt, wie die Darstellung nach der Figur zeigt, der Kolben 14 in jeder Betriebs-Verfahrstellung, auch in seiner gezeigten vordersten Endanschlagstellung beim Betrieb oder Gebrauch der Vorrichtung, im Gehäuse mit einer Druckkraft auf den weiteren Kolben 24 ein. Das Anschlußstück 26 verjüngt sich zum freien Ende des Gehäuse 10 hin absatzartig und ist außenumfangsseitig mit einem Anschlußgewinde 28 versehen, mit dem sich das Gehäuse 10 in der gezeigten Anordnung an ein Fluidsystem anschließen läßt, beispielsweise an die Diesel-Versorgungsleitung für ein Injektorsystem nach der Common-Rail-Technik. Das Gehäuse 10 befindet sich dabei in einer Anschlußleitung, die zu einer Hydropumpe, insbesondere Verdrängerpumpe, führt, beispielsweise in Form einer Dieselkraftstoffpumpe oder dergleichen. Die beim Betrieb der Dieselkraftstoffpumpe entstehenden Druckstöße, die bei Systemdrücken von bis zu 2200 bar und mehr erheblich sein können, sollen mit der erfindungsgemäßen Vorrichtung gedämpft und geglättet werden, wobei auch hochfrequente Fluidstöße ausgeglichen werden sollen. Ferner soll die erfindungsgemäße Dämpfungsvorrichtung auch bei sehr hohen Druckamplituden unabhängig hiervon in vorgebbaren Grenzbereichen wirksam sein. Das genannte Anschlußstück 26 geht in einen in der Länge verstärkten Boden 30 des Gehäuses 10 über und die genannten Kolben 14,24 sowie der Federspeicher 12 orientieren sich in ihrer Längsausrichtung an der Längsachse 32 von Gehäuse 10 und Anschlußstück 26. Des weiteren ist der Kol- ben 14 im Durchmesser um ein Mehrfaches größer als der Durchmesser des weiteren Kolbens 24, so dass im Hinblick auf die Änderung des Durchmesserverhältnisses eine sehr gute Stoßkrafteinleitung erfolgt zwischen weiterem Kolben 24 und erstem Kolben 16.The piston 14 cooperates with a further piston 24, the further piston 24 in this regard being guided so that it can move slowly in a connecting piece 26 of the housing 10. Furthermore, as the illustration according to the figure shows, the piston 14 acts on the further piston 24 in the housing with a compressive force in every operating travel position, also in its foremost end stop position shown during operation or use of the device. The connector 26 tapers towards the free end of the housing 10 and is provided on the outer circumference with a connection 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 a positive displacement pump, for example in the form of a diesel fuel pump or the like. The pressure surges that occur 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 using the device according to the invention, wherein high-frequency fluid surges are also to be compensated for. Furthermore, the damping device according to the invention is intended to be effective, even at very high pressure amplitudes, in predefinable limit ranges. Said connecting piece 26 merges into a lengthened bottom 30 of the housing 10 and the pistons 14, 24 and the spring accumulator 12 are oriented in their longitudinal orientation on the longitudinal axis 32 of the housing 10 and connecting piece 26. ben 14 in diameter several times larger than the diameter of the further piston 24, so that, with regard to the change in the diameter ratio, very good impact force is introduced between the further piston 24 and the first piston 16.
Der weitere Kolben 24 ist mithin in der Art eines Stempels oder Stößels ausgebildet und über mindestens eine Verliersicherung 34 in Form eines Sicherungsringes in der durchgehenden Gehäuseöffnung 36 des Anschlußstückes 26 geführt. Die Verliersicherung 34 kann dabei insbesondere aus einem Sicherungsring bestehen, der am vorderen Ende die Gehäuseöffnung 36 nach außen hin abschließt und an dessen Überstand das vordere Ende des weiteren Kolbens 24 in seiner vorderen Begrenzungslage anstößt. Im unbetätigten Zustand ist die Länge des weiteren Kolbens 24 derart bemessen, dass dieser mit einem geringen Spiel einen axialen Abstand zu der Verliersicherung 34 einhält. Sobald jedoch über den Kraftstoff ein vorgebbares Druckniveau aufgebaut ist, ist das Spiel beseitigt und im dahingehenden Betriebs- oder Gebrauchszustand der Vorrichtung übt dann der Kolben 14 in jeder Verfahrstellung des weiteren Kolbens 24 auf diesen eine Druckkraft aus. Um eine gute Abdichtung zu erreichen, ist der weitere Kolben 24 außenumfangsseitig derart feinstbearbeitet, insbesondere geläppt, dass ein metallisch dichter Spalt 38 zumindest zwischen Teilen des Außenumfanges des weiteren Kolbens 24 und der Innenwandung der Gehäuseöffnung 36 erreicht ist. Zur weiteren Verbesserung des Dichtsystems weist der weitere Kolben 24 außenumfangsseitig Ring- oder Schmiernuten 40 auf. Derartig ist eine Labyrinthdichtung erreicht, die es dem Dieselkraftstoff erschwert, über die Gehäuseöffnung 36 in den Zwischenraum 42 innerhalb des Gehäuses 10 zwischen Anlagefläche 20 und der ihr zugewandten Bodenfläche 44 des Bodens 30 einzudringen.The further piston 24 is thus designed in the manner of a plunger or plunger and is guided in the continuous housing opening 36 of the connecting piece 26 via at least one captive lock 34 in the form of a securing ring. The captive device 34 can in particular consist of a retaining ring which closes the housing opening 36 to the outside at the front end and on the projection of which the front end of the further piston 24 abuts in its front limiting position. In the unactuated state, the length of the further piston 24 is dimensioned such that it maintains an axial distance from the captive device 34 with a small amount of play. However, as soon as a predeterminable pressure level has been built up via the fuel, the play is eliminated and in the relevant operating or use state of the device, the piston 14 then exerts a compressive force on the additional piston 24 in each travel position. In order to achieve a good seal, the additional piston 24 is finely machined, in particular lapped, on the outer circumferential side in such a way that a metal-tight gap 38 is achieved at least between parts of the outer circumference of the additional piston 24 and the inner wall of the housing opening 36. To further improve the sealing system, the additional piston 24 has ring or lubrication grooves 40 on the outer circumferential side. In this way, a labyrinth seal is achieved, which makes it more difficult for the diesel fuel penetrate the housing opening 36 into the space 42 within the housing 10 between the contact surface 20 and the bottom surface 44 of the bottom 30 facing it.
In den genannten Fluid- oder Zwischenraum 42 zwischen den Kolben 14,24 mündet eine im Gehäuse 10 angeordnete Leckageöffnung 46 in der Art einer Bohrung und dergestalt kann ein bewußt vorgesehener Spalt- oder Leckagestrom über das Dichtsystem in Form der Ring- oder Schmiernuten 40, den metallischen Spalt 38 sowie den Zwischenraum 42 über die Lecka- geöffnung 46 auf die drucklose Leck- oder Tankseite des Gesamtsystems abgeführt werden. Als weiteres Dichtsystem ist im vorderen, stirnseitigen Bereich des Bodens 30 ein Dichtsystem 48 vorgesehen, beispielsweise in Form einer üblichen Ringdichtung. Bei eingeschraubtem Gehäuse 10 über das Anschlußstück 26 mit seinem Anschlußgewinde 28 läßt sich dergestalt eine Abdichtung, insbesondere in Form der Leckageöffnung 46, gegenüber dem gesamt hydraulischen- oder Fluidsystem (Diesel leitungsnetz) erreichen.A leakage opening 46 arranged in the housing 10 in the manner of a bore opens into the fluid or intermediate space 42 between the pistons 14, 24 and a deliberately provided gap or leakage stream can flow through the sealing system in the form of the ring or lubrication grooves 40 Metallic gap 38 and the space 42 are discharged through the leakage opening 46 to the unpressurized leak or tank side of the overall system. As a further sealing system, a sealing system 48 is provided in the front, front area of the base 30, for example in the form of a conventional ring seal. When the housing 10 is screwed in via the connecting piece 26 with its connecting thread 28, a seal, in particular in the form of the leakage opening 46, can be achieved with respect to the entire hydraulic or fluid system (diesel line network).
Als Federspeicher 12 dient im vorliegenden Fall eine Druckfeder in Form einer Schraubenfeder, wobei das Gehäuseinnere auch zusätzlich noch mit einem Druckgas, beispielsweise in Form eines Stickstoffgases, beaufschlagt sein kann. Die dahingehende Druckfeder 12 erstreckt sich zwischen dem Kolben 14 und einem Deckelteil 50, wobei das Deckelteil 50 aus einer Halteplatte 52 gebildet sein kann, die über ein Sicherungsmittel, insbesondere einen Sicherungsring 54, im Gehäuse 10 gehalten ist. Eine alternative Ausführungsform ist in der Figur in einer quadratischen Umrahmung wiedergegeben und im dahingehenden Fall besteht das Deckelteil 50 aus einem Schraubdeckel 56, der außenumfangsseitig über ein Außengewinde 58 des Gehäuses 10 auf dieses aufschraubbar ist. Mit der erfindungsgemäßen Vorrichtung ist sichergestellt, dass etwaig auftretende Leckageströme sicher beherrscht werden und aufgrund der getrennten Kolbenanordnung der Kolben 14 und 24 ist sichergestellt, dass es nicht zu Verkantungen kommt. Insbesondere sehr hochfrequente Druckstöße, die auf den stempelartigen weiteren Kolben 24 einwirken, lassen sich dergestalt in derselben Frequenz stoßartig an den Kolben 16 weitergeben, der unter dem Einfluß des Federspeichers 12 und unter Rückwirkung auf den weiteren Kolben 24 dann derart die Pulsationsdämpfung bzw. Pulsati- onsglättung vornimmt. Das gezeigte System läßt sich insbesondere auf der Gehäuseseite 10 aus üblichen Stahl Werkstoffen in kostengünstiger weise und fertigungstechnisch einfach realisieren. Die erfindungsgemäße Vorrichtung kann generell dort eingesetzt werden, wo geringe Volumen bei hohem Druck niveaugedämpft bzw. verschoben werden müssen. Durch die Flä- chenverhältnisse der Kolben kann die einzusetzende Feder kleiner aufbauen, da die erforderliche Kraft entsprechend reduziert wird. In the present case, a compression spring in the form of a helical spring serves as the spring accumulator 12, and the interior of the housing can also be acted upon with a compressed gas, for example in the form of a nitrogen gas. The relevant compression spring 12 extends between the piston 14 and a cover part 50, the cover part 50 being able to be formed from a holding plate 52 which is held in the housing 10 by means of a securing means, in particular a securing ring 54. An alternative embodiment is shown in the figure in a square frame and in this case the cover part 50 consists of a screw cover 56 which can be screwed onto the outer circumference via an external thread 58 of the housing 10. With the device according to the invention it is ensured that any leakage flows that occur are safely controlled and the separate piston arrangement of the pistons 14 and 24 ensures that canting does not occur. In particular, very high-frequency pressure surges, which act on the piston-like further piston 24, can be passed on to the piston 16 at the same frequency, which then under the influence of the spring accumulator 12 and with the effect on the further piston 24, the pulsation damping or pulsation ons smoothing. The system shown can be implemented, in particular, on the housing side 10 from conventional steel materials in a cost-effective manner and is easy to manufacture. The device according to the invention can generally be used where small volumes have to be level-damped or shifted at high pressure. Due to the area ratio of the pistons, the spring to be used can be smaller, since the required force is reduced accordingly.

Claims

P a t e n t a n s p r ü c h e Patent claims
1. Vorrichtung zum Dämpfen von Druckstößen in einem Fluid mit einem Gehäuse (10) und einem gegen die Vorspannkraft eines Federspeichers (12) in dem Gehäuse (10) langsverfahrbaren Kolben (14), dadurch gekennzeichnet, dass der Kolben (14) mit einem weiteren Kolben (24) zusammenwirkt, der in einem Anschlußstück (26) des Gehäuses (10) langsverfahrbar geführt ist, und dass beim Betrieb der Vorrichtung der Kolben (14) in jeder Verfahrstellung des weiteren Kolbens (24) auf die- sen eine Druckkraft ausübt.1. Device for damping pressure surges in a fluid with a housing (10) and a piston (14) which can be moved slowly against the biasing force of a spring accumulator (12) in the housing (10), characterized in that the piston (14) with another Piston (24) cooperates, which is guided in a connection piece (26) of the housing (10) so that it can move slowly, and that, when the device is operated, the piston (14) exerts a compressive force on the piston (24) in every travel position.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Kolben (14) im Durchmesser um ein Mehrfaches größer ist als der Durchmesser des weiteren Kolbens (24).2. Device according to claim 1, characterized in that the piston (14) is several times larger in diameter than the diameter of the further piston (24).
3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der weitere Kolben (24) in der Art eines Stempels ausgebildet ist und über mindestens eine Verliersicherung (34) in einer durchgehenden Gehäuseöffnung (36) des Anschlußstückes (26) geführt ist.3. Device according to claim 1 or 2, characterized in that the further piston (24) is designed in the manner of a stamp and is guided via at least one anti-loss device (34) in a continuous housing opening (36) of the connecting piece (26).
4. Vorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der weitere Kolben (24) außenumfangsseitig derart fei nstbearbeitet, insbesondere geläppt ist, dass ein metallisch dichter Spalt (38) zumindest zwischen Teilen des Außenumfanges des weiteren Kolbens (24) und der Innen- wandung der Gehäuseöffnung (36) erreicht ist.4. The device according to claim 3, characterized in that the further piston (24) is finely machined, in particular lapped, on the outer circumferential side such that a metal-tight gap (38) at least between parts of the outer circumference of the further piston (24) and the inner wall the housing opening (36) is reached.
5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass der weitere Kolben (24) außenumfangsseitig mit Ring- oder Schmiernuten (40) versehen ist. 5. Device according to one of claims 1 to 4, characterized in that the further piston (24) is provided on the outer peripheral side with ring or lubrication grooves (40).
6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass in den Fluidraum (42) zwischen den Kolben (14,24) eine im Gehäuse (10) angeordnete Leckageöffnung (46) mündet.6. Device according to one of claims 1 to 5, characterized in that a leakage opening (46) arranged in the housing (10) opens into the fluid space (42) between the pistons (14, 24).
7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass als Federspeicher (12) mindestens eine als Druckfeder ausgebildete Schraubenfeder und/oder ein Druckgas dient.7. Device according to one of claims 1 to 6, characterized in that at least one helical spring designed as a compression spring and / or a compressed gas is used as the spring accumulator (12).
8. Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, dass die Druckfeder (12) sich zwischen dem Kolben (14) und einem Deckelteil (50) innerhalb des Gehäuses erstreckt.8. The device according to claim 7, characterized in that the compression spring (12) extends between the piston (14) and a cover part (50) within the housing.
9. Vorrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeich- net, dass das Deckelteil (50) aus einer Halteplatte (52) gebildet ist, die über ein Sicherungsmittel, insbesondere Sicherungsring (54), im Gehäuse (10) gehalten ist oder dass das Deckelteil (50) aus einem Schraubdeckel (56) besteht, der außenumfangsseitig über ein Außengewinde (58) des Gehäuses (10) auf dieses aufschraubbar ist.9. Device according to one of claims 1 to 8, characterized in that the cover part (50) is formed from a holding plate (52) which is held in the housing (10) via a securing means, in particular a securing ring (54), or that the cover part (50) consists of a screw cover (56) which can be screwed onto the outer circumference via an external thread (58) of the housing (10).
10. Vorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, dass das Anschlußstück (26) des Gehäuses (10), in dem der weitere Kolben (24) geführt ist, im Außendurchmesser gegenüber dem Außendurchmesser des Gehäuses (10) reduziert ist. 10. Device according to one of claims 1 to 9, characterized in that the connecting piece (26) of the housing (10), in which the further piston (24) is guided, is reduced in outer diameter compared to the outer diameter of the housing (10).
EP04790081A 2003-10-31 2004-10-01 Device for damping pressure surges Expired - Lifetime EP1685323B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10350941A DE10350941A1 (en) 2003-10-31 2003-10-31 Device for damping pressure surges
PCT/EP2004/010971 WO2005052348A1 (en) 2003-10-31 2004-10-01 Device for damping pressure surges

Publications (2)

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EP1685323A1 true EP1685323A1 (en) 2006-08-02
EP1685323B1 EP1685323B1 (en) 2010-06-23

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EP04790081A Expired - Lifetime EP1685323B1 (en) 2003-10-31 2004-10-01 Device for damping pressure surges

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

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Also Published As

Publication number Publication date
WO2005052348A1 (en) 2005-06-09
US20060225800A1 (en) 2006-10-12
US7308910B2 (en) 2007-12-18
ATE472053T1 (en) 2010-07-15
DE502004011318D1 (en) 2010-08-05
EP1685323B1 (en) 2010-06-23
JP2007511695A (en) 2007-05-10
DE10350941A1 (en) 2005-06-02

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