EP2616665A1 - Compensateur de température hydraulique et élément de transmission de course hydraulique - Google Patents

Compensateur de température hydraulique et élément de transmission de course hydraulique

Info

Publication number
EP2616665A1
EP2616665A1 EP11749802.2A EP11749802A EP2616665A1 EP 2616665 A1 EP2616665 A1 EP 2616665A1 EP 11749802 A EP11749802 A EP 11749802A EP 2616665 A1 EP2616665 A1 EP 2616665A1
Authority
EP
European Patent Office
Prior art keywords
chamber
hydraulic
wall
temperature compensator
sub
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
EP11749802.2A
Other languages
German (de)
English (en)
Other versions
EP2616665B1 (fr
Inventor
Georg Bachmaier
Gerit Ebelsberger
Bernhard Fischer
Michael HÖGE
Erhard Magori
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Priority to PL11749802T priority Critical patent/PL2616665T3/pl
Priority to EP15001834.9A priority patent/EP2947308B1/fr
Publication of EP2616665A1 publication Critical patent/EP2616665A1/fr
Application granted granted Critical
Publication of EP2616665B1 publication Critical patent/EP2616665B1/fr
Active 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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/06—Details
    • F15B7/10—Compensation of the liquid content in a system
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms
    • 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
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/705—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for filling or emptying hydraulic chamber, e.g. for compensating clearance or thermal expansion
    • 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
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F02M2200/708—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with hydraulic chambers formed by a movable sleeve
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2514—Self-proportioning flow systems
    • Y10T137/2516—Interconnected flow displacement elements

Definitions

  • the invention relates to a hydraulic temperature compensator, in particular for a hydraulic Hubübertrager.
  • the invention further relates to a hydraulic lifting transformer with such a hydraulic temperature compensator, in particular an injector.
  • injector For introducing a desired amount of fuel in any combustion process are usually injector (Injek ⁇ factors) needed by means of which metering an amount of fuel is bar. Since many combustion processes proceed with the direct ⁇ injection of highly pressurized fuel, often particularly fast operating actuators are set a ⁇ which drive injector. This means that an actuator generates a stroke which actuates, for example, an injector needle, which in turn opens a valve and releases a fuel at predetermined time intervals and in adjustable flow rates for a combustion process. Combustion air is supplied separately ⁇ leads in this case.
  • Injectors for high-pressure direct injection often use fast actuators, such as "Piezo Multilayer Actuators” (PMA). These are solid state actuators whose central element consists of a plurality of piezoelectric layers. Furthermore, so-called magnetostrictive solid state actuators are known which exploit a magneto-mechanical effect for the generation of a stroke. For the generation of a stroke is important that such Festkör ⁇ peractors have too low a stroke to open a In ektor- needle so far that the desired amount of fuel is introduced. Especially with gas injectors that require a longer stroke than injectors that dose liquid fuel, this becomes a major problem. This results in only constructions with a stroke translator being considered.
  • PMA piezo Multilayer Actuators
  • An increase in the stroke of an actuator with a transla ⁇ wetting of less than 1: 2 is often implemented with mechanical levers.
  • the mechanical transmission ratio can be 1: 1.6.
  • Gas injectors typically require larger ratios.
  • hydraulicmaschineset ⁇ zer also referred to as hydraulic levers used.
  • CNG direct injection compressed natural gas
  • a disadvantage of the prior art is, for example, in motor vehicle technology the wide Temperaturbe ⁇ rich, which can range from - 40 C ° to + 150 C °. This can bring in the consideration of significant volumes of liquid Volu ⁇ menver base urge with it. Peak values can be significantly higher than 30% volume increase. For this reason, hydraulic stroke translators in most cases require connection to a reservoir.
  • German patent application DE 10 2005 042 786 AI for example, a fuel injector is disclosed, which is equipped with a hermetically sealed hydraulic system.
  • so-called guided pistons are used.
  • Such guided pistons require high mechanical precision in manufacturing and are very susceptible to wear.
  • a hydraulic temperature compensator at least comprising a lekssausdehnbare Hyd ⁇ raulikhunt and a gas-filled chamber of the hydraulic is at least partially surrounded, wherein the hydrau ⁇ likhunt is divided into a first sub-chamber and a second sub-chamber, which are hydraulically connected to each other by means of at least one throttle point and wherein the second sub-chamber adjacent to the gas-filled chamber.
  • a pressure of a liquid in the hydraulic chamber also rises slowly due to its thermal expansion.
  • the first sub-chamber and the second sub-chamber are fluidically ver ⁇ bound by the throttle point virtually unhindered. Due to the increase in pressure in the liquid and the consequent larger pressure difference between the second sub-chamber and the gas-filled chamber, the (internal) gas-filled chamber is compressed so that the liquid can expand and the pressure increase of the liquid is limited, in particular to a practically negligible level , This process is friction-free and therefore lock-free.
  • the pressure limitation can insbesonde ⁇ re also be used for fluidly connected to the hydraulic chamber, in particular with the first sub-chamber, connected hydraulic elements or devices.
  • a pressure in particular via the first sub-chamber, can be passed on essentially without loss, or, e.g. By a compression of the temperature compensator, constructed essentially lossless and possibly passed on.
  • the temperature compensator is thus particularly suitable for use in or with fast-switching Hubübertragern (hydraulic levers) and actuators.
  • the temperature compensator is largely friction-free and therefore operable without closure and allows both ei ⁇ nen effective temperature compensation as well as a widespread lossless pressure transfer and / or pressure build-up.
  • the temperature compensator also has a particularly compact design.
  • the throttle may be designed with a suitably dimensioned flow cross-section for example, as a diesstechnikska ⁇ nal (eg in the form of a hole).
  • the gas-filled chamber is an open chamber.
  • the gas-filled chamber may be to insbeson ⁇ broader connected by a passage opening to the environment of temperature turkompensators.
  • the gas-filled chamber may be hermetically sealed.
  • the gas may be air, so the gas-filled chamber may be an air chamber.
  • the hydraulic chamber is formed by means of an inner wall which is used contactlessly in an outer wall,
  • a partition wall for forming the first sub-chamber and the second sub-chamber is used without contact and the partition wall having at least one throttle point
  • the inner wall, the outer wall and the partition are each open on one side and are hermetically fixed with their respective open side to a common cover, and
  • the gas-filled chamber is formed by means of an inner side of the inner ⁇ wall.
  • This embodiment is particularly simple and robust construction ⁇ bar.
  • a deformation of the temperature compensator and a resulting pressure build-up in a rapid deformation can be achieved easily by a relative displacement of the lid.
  • the partition may be formed in particular rigid.
  • the inner wall and the outer wall may be lekssausdehn ⁇ bar (compressible / expandable) in particular.
  • the inner wall can be as integrated into the outer wall be ⁇ wrote.
  • the inner wall and / or the outer wall are each in the form of an end offe ⁇ nen bellows, in particular metal bellows, designed.
  • the bellows has the advantage that it is much easier than perpendicular to stretchable in a longitudinal extension (particularly compressible and re-expandable), and these Ver ⁇ design moldability is technically easy to reach.
  • bellows are inexpensive to produce and easy to handle and fasten.
  • the partition in the form of an open end (rigid) hollow cylinder (with any, advantageously circular, cross-section) is configured.
  • This has the advantage that a Volu ⁇ men in the first partial chamber is substantially only dependent on a deformation of the outer metal bellows and depends on a volume of the second partial chamber substantially only from a deformation of the inner metal bellows, and the two volumes only through the orifice interact with each other.
  • bellows and the partition are arranged concentrically to a common axis.
  • the outer wall is hermetically fixed to the partition wall and the partition wall is hermetically fixed to the lid.
  • the outer wall is thus fastened directly to the lid.
  • the outer wall and the dividing wall can be fastened hermetically individually (directly) to the lid.
  • at least one compression spring element is accommodated in the gas-filled chamber. This provides the advantage that a (static) system pressure can be adjusted in the hydraulic fluid. Also, such a relationship between a pressure difference between the second sub-chamber and the gas-filled chamber on the one hand and a change in volume of the second sub-chamber is particularly precisely adjustable.
  • the spring force of the spring element can also by means of an actuating element projecting into the gas-filled chamber, e.g. a set screw, individually and subsequently adjustable. This allows the system pressure to be changed later.
  • the hydraulic chamber has a unidirectional valve, in particular flutter valve, on ⁇ which allows a flow from the second sub-chamber into the first sub-chamber. This can shorten ver ⁇ ⁇ a dead interim rule two compression stages of the temperature compensator.
  • the hydraulic chamber is filled with a substantially incompressible fluid, in particular with oil, in particular hydraulic oil, in particular ⁇ sondere bubbles. This can be achieved by a vacuum filling . So lift and / or pressure losses can be suppressed.
  • a hydraulic lifting transformer comprising at least the hydraulic temperature compensator as described above, a stroke actuator acting on the temperature compensator and a further hydraulic chamber which is fluidically connected to the first subchamber of the hydraulic chamber of the temperature compensator, wherein the further Hydraulic chamber is fluidly connected to a displaceably mounted actuator in connection.
  • the hydraulic lift transformer can also be designed as a hydraulic lever.
  • the hydraulic lift transformer can also be configured as a valve, in particular an injection valve.
  • the hydraulic chamber is formed by a non-contact used in an outer wall inner wall, between the outer wall and the inner wall, a partition wall for forming the first sub-chamber and the second sub-chamber is used without contact and the partition, the at least one Throttle ⁇ site has, the inner wall, the outer wall and the partition ⁇ each wall are open and are hermetically attached with their respective open side to a common cover and the gas-filled chamber is formed by an inner side of the inner wall, the Hubaktor can in particular with the Cover be connected. So a largely ver ⁇ lossless Hubaufbringung is made possible on the hydraulic temperature compensator.
  • the stroke transformer is part of an injector.
  • the injector may be, for example, a liquid injector (for example a diesel, kerosene, LPG or gasoline injector) or a gas injector.
  • spatter for example, a hydrogen injector or natural gas injector.
  • the hydraulic stroke transmitter may be seen to Studentstra ⁇ gen of Primärhubs of Hubaktors provided on an actuator ⁇ in particular.
  • the hydraulic lift transmitter may be a hydraulic lift converter.
  • the hydraulic lift transformer may be a hydraulic Hubuntersetzer.
  • the Hubaktor, the inner wall, the outer wall and the partition can be arranged concentrically to each other.
  • Ele ⁇ elements may be provided with the same reference numerals for clarity.
  • FIG. 1 shows a sectional side view of a hydraulically driven valve with a thermal compensator according to the invention according to a first embodiment
  • FIG. 2 shows a sectional side view of a thermal compensator according to the invention according to a second embodiment
  • FIG 3 shows a sectional side view of a thermal compensator according to the invention according to a third embodiment.
  • Fig.l outlines a hydraulically driven valve 1, in ⁇ example, an injector, in particular a fuel ⁇ injector.
  • the valve 1 has a solid-lifting actuator in the form of a piezoelectric actuator 2, which rests with its back on a bearing 3 and on its front side has a plunger 4.
  • the plunger 4 is along a body axis or longitudinal axis L displaceable.
  • the plunger 4 is hinged to a thermal compensator 5 according to a first embodiment.
  • the thermal compensator 5 has an outer wall in the form of egg ⁇ nes one-sided open outer metal bellows 6. In the äuße ⁇ ren metal bellows 6 a smaller in length and diameter inner metal bellows 7 is used, which is also open at the end.
  • a partition wall 8 in the form of a rigid, open-ended hollow cylinder.
  • the outer metal ⁇ bellows 6, the inner metal bellows 7 and the partition wall 8 are substantially rotationally symmetrical about a respective longitudinal axis L and arranged concentrically to the body axis of the piezo zoaktors.
  • a throttle point 24 In the partition wall 8 is a throttle point 24 which connects the first sub-chamber 10 with the second sub-chamber 11.
  • the outer metal bellows 6, the inner metal bellows 7 and the partition 8 are at least laterally (with respect to.
  • the outer metal bellows 6, the inner metal bellows 7 and the partition wall 8 are aligned so that their open Endflä ⁇ surfaces or end faces in the direction of a cover 9 and an end plate have.
  • the outer metal bellows 6, the inner metal ⁇ bellows 7 and the partition 8 are special fixed with their open sides into ⁇ directly or indirectly on the lid. 9
  • the inner metal bellows 7 is fixed with its ⁇ of fenen side and with its free edge sealed and fixed to the cover 9, for example. B. by means of a welded connection.
  • the outer metal bellows 6 is hermetically mounted on a side table überste ⁇ Henden edge region of the free edge of the partition wall 8, for example by a welded joint.
  • the outer metal bellows 6 and the partition wall 8 thus form a first partial chamber 10.
  • the partition wall 8 is also fastened with its free edge to the cover 9, namely laterally outside with respect to the inner metal bellows 7, for example by means of a welded connection.
  • the inner metal bellows 7, the partition wall 8 and the cover 9 form a second sub-chamber 11.
  • the gas-filled chamber 12 formed by an inner volume of the second metal bellows 7 is thus separated from the second sub-chamber 11 only by the second metal bellows 7.
  • the gas-filled chamber 12 does not have to be hermetically sealed relative to an environment of the valve 1 and, for example, may be pneumatically open with the environment via one or more passage openings (FIG.
  • the plunger 4 is thus guided on an outer side of the lid 9, and a lid region 9 opposite bottom portion
  • the thermal compensator 5 and the piezoelectric actuator 2 are therefore connected mechanically in series and inserted between the two fixed bearings 3, 14.
  • the thermal compensator 5 has at its outer metal bellows 6 to a hydraulic connection 15, to which here a provided with a throttle 16 hydraulic line 17 is connected.
  • the hydraulic line 17 leads to a further metal bellows 18 which encloses a further hydraulic chamber 18a filled with the hydraulic fluid H.
  • the metal ⁇ bellows 18 is rearwardly connected to a further fixed bearing 19 and is located thereon.
  • An open end of the metal bellows 18 is closed by an actuator in the form of a secondary plunger 20.
  • the secondary plunger 20 is mounted linearly displaceable and is urged by means of a spring element 21 in the further metal bellows 18.
  • the secondary plunger 20 is provided as an actuator for opening or closing a valve element 22 which can selectively open or close a fluid line 23, eg, a fuel supply line to a combustion chamber of an engine.
  • the secondary plunger 20 may be integrated into the valve 22 or constitute a part of this valve 22.
  • the first sub-chamber 10, the second sub-chamber 11, the hydraulic line 17 and the further metal bellows 18 are filled with a substantially incompressible hydraulic fluid H.
  • the hydraulic fluid H may be, for example, a hydraulic oil.
  • the incompressibility can be example ⁇ be assisted by a vacuum filling.
  • the valve 1 between the lift actuator 2 and the secondary plunger 20 may also be referred to as a hydraulic lever.
  • Spring element 21 is extended and the valve 22 switch, for example, open, can.
  • the primary plunger 4 is moved back again by the spring force of the outer metal bellows 6 and the pressure in the hydraulic fluid H decreases again.
  • the secondary plunger 20 is also pushed back into the metal bellows 18 by the spring element 21. one shifted, so that a switching position of the valve 22 is reset again, the valve 22, for example as ⁇ closed.
  • the hydraulic temperature compensator 5 thus serves to build up pressure in the valve 1.
  • the pressure of the hydraulic fluid due to a temperature ⁇ H stretch will increase slowly.
  • This increases a pressure difference between the second sub-chamber 11 and the gas-filled chamber 12, so that the gas-filled chamber 12 is compressed by a compression of the second metal bellows 7 along the longitudinal axis L and correspondingly increases the volume of the second sub-chamber 11.
  • the gas-filled chamber 12 thus serves as Ausretesvo ⁇ lumen for compensating a temperature-induced volume expansion of the hydraulic fluid H.
  • FIG. 2 shows a sectional side view of a hydraulic temperature compensator 25 according to a second From leadership form, which, for example, instead of the hydraulic ⁇ temperature compensator 5 in the valve 1 can be installed.
  • the hydraulic temperature compensator 25 has an additional compression spring 26 in the gas-filled chamber 12 in relation to the hydraulic temperature compensator 5.
  • Compression spring is designed here as a spiral spring which is supported on the one hand on the cover 9 and on the other hand on a Bo ⁇ den 27 of the inner metal bellows 7.
  • the inner metal bellows 7 is stretched more, and it is functionally stiffened against deformation in the longitudinal direction.
  • the compression spring 26 that the Sys ⁇ temtik of the hydraulic fluid increases.
  • Druckfe ⁇ of 26 may further include a ratio between a change in pressure of the hydraulic fluid H and an associated volume menveriererung be adjusted very accurately to the second part chamber 11, and thus a relationship between a pressure level of the hydraulic fluid H and a temperature of the hydraulic fluid H.
  • FIG. 3 shows a sectional side view of a hydraulic temperature compensator 28, which can be inserted into the valve 1 instead of the hydraulic temperature compensator 5, for example.
  • the hydraulic Temperaturkompensa ⁇ gate 28 in contrast to the hydraulic Temperaturkom- expansion joint 5 to the partition wall to a flutter valve 29 having an associated flap 30 on a layer adjacent to the first partial chamber 10 outside of the partition wall. 8
  • the flutter ⁇ valve 29 causes a "dead time" between two Actu ⁇ tions of the piezoelectric actuator 2 is reduced during normal operation. Because each time the piezoactuator 2 pushes the cover 9 down over the plunger 4, the pressure increases as described in the first sub-chamber 10.
  • the flutter valve 29 (or any other geeig ⁇ designated unidirectional valve which has a comparatively large flow cross-section and the Hydraulikflüs ⁇ stechnik leaves from the second sub-chamber 11 in the first Partkamm- mer 10 therethrough) accelerates this pressure equalization, and enables faster re-activation of the Piezoaktors 2 and the plunger 4th
  • the thermal temperature compensator 5, 25, 28 may be manufactured separately and installed and filled as a unit in the valve 1.
  • the hydraulic temperature compensator may be further integrated in the valve 1, for example, characterized in that the outer metal bellows 6 and the metal bellows 18 present as an only peo ⁇ ger metal bellows and therefore the control element 20 single ⁇ Lich by the hydraulic fluid H from the second metal bellows 7 would be separated.
  • the Hydrauliklei ⁇ device 17 could be omitted, and it is a valve with a particularly compact design achievable.
  • features of the different embodiments may be combined, e.g. for a hydraulic temperature compensator with a compression spring in the gas-filled chamber and in addition a unidirectional valve in the partition wall.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Damping Devices (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention porte sur un compensateur de température hydraulique (5) qui présente au moins une chambre hydraulique (10, 11) qui peut être mise en extension en longueur et une chambre remplie de gaz (12) qui est entourée au moins partiellement par la chambre hydraulique (10, 11), la chambre hydraulique (10, 11) étant divisée en une première chambre partielle (10) et une deuxième chambre partielle (11), qui sont reliées hydrauliquement l'une à l'autre par au moins un étranglement (24) et la deuxième chambre partielle (11) étant limitée au niveau de la chambre remplie de gaz (12). L'unité de transmission de course (1) présente au moins le compensateur de température hydraulique, un actionneur de course (2) agissant sur le compensateur de température (5) et une autre chambre hydraulique (18a) qui est reliée fluidiquement à la première chambre partielle (10) de la chambre hydraulique (10, 11) du compensateur de température (5), l'autre chambre hydraulique (18a) étant en communication fluidique avec un élément de réglage (20) mobile en translation.
EP11749802.2A 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique Active EP2616665B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL11749802T PL2616665T3 (pl) 2010-09-13 2011-08-22 Hydrauliczny kompensator temperatury i hydrauliczny przenośnik skoku
EP15001834.9A EP2947308B1 (fr) 2010-09-13 2011-08-22 Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010040612 DE102010040612A1 (de) 2010-09-13 2010-09-13 Hydraulischer Temperaturkompensator und hydraulischer Hubübertrager
PCT/EP2011/064362 WO2012034823A1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP15001834.9A Division-Into EP2947308B1 (fr) 2010-09-13 2011-08-22 Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique
EP15001834.9A Division EP2947308B1 (fr) 2010-09-13 2011-08-22 Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique

Publications (2)

Publication Number Publication Date
EP2616665A1 true EP2616665A1 (fr) 2013-07-24
EP2616665B1 EP2616665B1 (fr) 2016-01-20

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP11749802.2A Active EP2616665B1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique
EP15001834.9A Active EP2947308B1 (fr) 2010-09-13 2011-08-22 Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP15001834.9A Active EP2947308B1 (fr) 2010-09-13 2011-08-22 Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique

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US (1) US9488194B2 (fr)
EP (2) EP2616665B1 (fr)
DE (1) DE102010040612A1 (fr)
HU (1) HUE027360T2 (fr)
PL (1) PL2616665T3 (fr)
WO (1) WO2012034823A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102010040612A1 (de) 2010-09-13 2012-03-15 Siemens Aktiengesellschaft Hydraulischer Temperaturkompensator und hydraulischer Hubübertrager
US9091240B2 (en) 2013-01-24 2015-07-28 Caterpillar Inc. Compressed natural gas fuel mass control system
DE102016208773A1 (de) * 2016-05-20 2017-11-23 Siemens Aktiengesellschaft Piezohydraulischer Aktor
RU2701473C1 (ru) * 2018-09-14 2019-09-26 Общество с ограниченной ответственностью "Производственная компания "РОСНА Инжиниринг" Стенд для испытаний механического теплового компенсатора
EP3956569A1 (fr) * 2019-04-17 2022-02-23 MetisMotion GmbH Unité de transmission hydraulique pour un dispositif actionneur

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JPH0656162B2 (ja) 1987-03-03 1994-07-27 トヨタ自動車株式会社 ストロ−ク可変装置
DE29708546U1 (de) 1997-05-14 1998-09-10 Fev Motorentech Gmbh & Co Kg Elektrischer Festkörperaktuator mit hydraulischer Übersetzung
DE19958704C2 (de) * 1999-12-06 2002-10-02 Siemens Ag Vorrichtung zum Übertragen einer Aktorbewegung und Fluiddosierer mit einer solchen Vorrichtung
DE19962177A1 (de) 1999-12-22 2001-07-12 Siemens Ag Hydraulische Vorrichtung zum Übertragen einer Aktorbewegung
DE10321693A1 (de) * 2003-05-14 2004-12-02 Robert Bosch Gmbh Brennstoffeinspritzventil
DE602005005242T2 (de) 2004-04-26 2009-04-02 Isuzu Motors Ltd. Längen-Ausgleichselement und dieses enthaltendes Kraftstoff-Einspritzventil
DE102004021920A1 (de) * 2004-05-04 2005-12-01 Robert Bosch Gmbh Brennstoffeinspritzventil
JP4641387B2 (ja) * 2004-06-01 2011-03-02 日産自動車株式会社 流体継手
DE102004060533A1 (de) 2004-12-16 2006-06-29 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102005042786B4 (de) 2005-09-08 2009-04-16 Siemens Ag Kraftstoffinjektor mit hermetisch abgedichtetem Hydrauliksystem
DE502007002482D1 (de) * 2007-03-15 2010-02-11 Ford Global Tech Llc Injektor
US8267675B2 (en) * 2008-06-16 2012-09-18 GM Global Technology Operations LLC High flow piezoelectric pump
DE102010040612A1 (de) 2010-09-13 2012-03-15 Siemens Aktiengesellschaft Hydraulischer Temperaturkompensator und hydraulischer Hubübertrager

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Publication number Publication date
US20130269790A1 (en) 2013-10-17
EP2616665B1 (fr) 2016-01-20
PL2616665T3 (pl) 2016-07-29
WO2012034823A1 (fr) 2012-03-22
US9488194B2 (en) 2016-11-08
EP2947308B1 (fr) 2017-09-27
HUE027360T2 (en) 2016-09-28
DE102010040612A1 (de) 2012-03-15
EP2947308A1 (fr) 2015-11-25

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