EP2947308B1 - Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique - Google Patents

Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique Download PDF

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Publication number
EP2947308B1
EP2947308B1 EP15001834.9A EP15001834A EP2947308B1 EP 2947308 B1 EP2947308 B1 EP 2947308B1 EP 15001834 A EP15001834 A EP 15001834A EP 2947308 B1 EP2947308 B1 EP 2947308B1
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EP
European Patent Office
Prior art keywords
chamber
hydraulic
sub
temperature compensator
metal bellows
Prior art date
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Application number
EP15001834.9A
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German (de)
English (en)
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EP2947308A1 (fr
Inventor
Georg Dr. Bachmaier
Gerit Ebelsberger
Bernhard Fischer
Michael Dr. Höge
Erhard Dr. Magori
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Siemens AG
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Siemens AG
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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 lifting transformer with a hydraulic temperature compensator, in particular an injector.
  • injectors To introduce a desired amount of fuel in any combustion processes injection usually (injectors) are necessary, by means of which an amount of fuel can be metered. Since many combustion processes occur with the direct injection of high-pressure fuel, often very fast-acting actuators are used, which drive injectors. 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 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 magnetic mechanical effect for the generation of a stroke. For the generation of a stroke is important that such solid state actuators have too low a stroke to open an injector needle so far that the desired amount of fuel is introduced. Especially with gas injectors that require a longer stroke than injectors that meter liquid fuel, this becomes a major issue Problem. This means that only constructions with a Hubübersetzer come into question.
  • an increase in the stroke of an actuator with a ratio of less than 1: 2 is often realized with mechanical levers.
  • the mechanical transmission ratio can be 1: 1.6.
  • Gas injectors typically require larger ratios.
  • hydraulic translators also referred to as hydraulic levers used.
  • CNG direct injection compressed natural gas uses a 1: 6 stroke ratio.
  • the idle stroke can be avoided, so that the chain of action between the actuator and the nozzle needle is constantly present. This is reflected directly in the structural design. In other words, the Aktorauslenkung is exploited to a greater extent from the injector and implemented.
  • German Offenlegungsschrift DE 10 2005 042 786 A1 For example, a fuel injector is disclosed that is equipped with a hermetically sealed hydraulic system. In this document so-called guided pistons are used. Such guided pistons require high mechanical precision in manufacturing and are very susceptible to wear.
  • Another example is from the DE 199 58 704 A1 known.
  • a hydraulic temperature compensator at least comprising a lekssausdehnbare hydraulic chamber and a gas filled chamber coming from the hydraulic chamber is at least partially surrounded, wherein the hydraulic chamber 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.
  • the first sub-chamber and the second sub-chamber are fluidically connected through 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 (inner) 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 also be used for fluidically connected hydraulic elements or devices with the hydraulic chamber, in particular with its first sub-chamber.
  • a pressure in particular via the first sub-chamber, can be passed on essentially without loss, or, e.g. be constructed by a compression of the temperature compensator, 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 frictionless and therefore operable without seal and allows both an effective temperature compensation and a largely lossless pressure transfer and / or pressure build-up.
  • the temperature compensator also has a particularly compact design.
  • the restriction may be configured as a fluid channel (e.g., in the form of a bore) having a suitably sized flow area.
  • the gas-filled chamber is an open chamber.
  • the gas-filled chamber can be connected in particular via a passage opening to the surroundings of the temperature compensator.
  • the gas-filled chamber may be hermetically sealed.
  • the gas may be air, so the gas-filled chamber may be an air chamber.
  • This embodiment is particularly simple and robust to build.
  • 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 in particular be longitudinally expandable (compressible / expandable).
  • the inner wall can also be described as integrated into the outer wall.
  • the inner wall and / or the outer wall in each case in the form of an end open bellows, in particular metal bellows, are configured.
  • the bellows has the advantage that in a longitudinal extension it is much easier to stretch (in particular compressible and re-expandable) than perpendicular to it and this deformability is easily achievable in terms of design technology.
  • 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 volume in the first sub-chamber essentially depends only on a deformation of the outer metal bellows and a volume in the second sub-chamber essentially depends only on a deformation of the inner metal bellows and the two volumes only through the throttle point with each other in Active compound stand.
  • 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 indirectly attached to the lid.
  • the outer wall and the partition wall may be individually (directly) hermetically attached to the lid.
  • At least one compression spring element is accommodated in the gas-filled chamber.
  • a (static) system pressure can be adjusted in the hydraulic fluid.
  • 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, which allows a flow from the second sub-chamber into the first sub-chamber. As a result, a dead time between two compression phases of the temperature compensator can be shortened.
  • the hydraulic chamber is filled with a substantially incompressible liquid, in particular with oil, in particular hydraulic oil, in particular free of 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 sub-chamber of the hydraulic chamber of the temperature compensator, wherein the further hydraulic chamber fluidly is in communication with a displaceably mounted actuator.
  • 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 has the at least one throttle point in that the inner wall, the outer wall and the partition wall are each open on one side and are hermetically fixed with their respective open side to a common lid and the gas-filled chamber is formed by an inner side of the inner wall, the Hubaktor can be connected in particular to the lid. This allows a largely lossless stroke application to the hydraulic temperature compensator.
  • the stroke transformer is part of an injector.
  • the injector can be, for example, a liquid injector (for example a diesel, kerosene, LPG or gasoline injector) or a gas injector (For example, a hydrogen injector or natural gas injector).
  • the hydraulic lift transformer may be provided in particular for transmitting the Primärhubs the Hubaktors on an actuator.
  • 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.
  • Fig.1 outlined a hydraulically driven valve 1, for 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 articulated to a thermal compensator 5 according to a first embodiment.
  • the thermal compensator 5 has an outer wall in the form of a unilaterally open outer 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 with the body axis of the piezoelectric actuator 2.
  • 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 dividing wall 8 are at least laterally spaced apart (with respect to the body axis of the piezoactuator 2 and the longitudinal axis L, respectively).
  • the outer metal bellows 6, the inner metal bellows 7 and the partition wall 8 are aligned so that their open end faces or end faces point in the direction of a cover 9 and an end plate, respectively.
  • the outer metal bellows 6, the inner metal bellows 7 and the partition wall 8 are fastened with their open sides in particular directly or indirectly to the cover 9. More specifically, here is the inner metal bellows 7 hermetically and firmly attached to the lid 9 with its open side or with its free edge, z. B. by means of a welded connection.
  • the outer metal bellows 6 is hermetically attached to a laterally projecting edge region of the free edge of the partition 8, for example by a welded connection.
  • 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, e.g. by means of a welded joint.
  • 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 need not be hermetically sealed relative to an environment of the valve 1 and may be pneumatically open, for example, with the environment via one or more through-openings (o.Fig.).
  • the plunger 4 is thus articulated on an outer side of the lid 9, and a cover 9 of the opposite bottom portion 13 of the outer metal bellows 6 is connected to a further fixed bearing 14.
  • 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 or lies on it.
  • 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 supported for example 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.
  • the plunger 4 is relatively quickly extended or moved in the direction of the cover 9. Since the piezoelectric actuator 2 is supported rearwardly by the fixed bearing, the cover 9 is displaced in the direction of the bellows 6, 7 and the partition 8. Since the bottom 13 of the outer metal bellows 6 is supported on the fixed bearing 14, the movement of the cover 9 compresses the outer metal bellows 6 in the longitudinal direction. Due to the comparatively fast movement of the lifting plunger 4 occurs during its actuation time only a small, practically insignificant amount of hydraulic fluid H through a throttle point 24th
  • 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 again in the metal bellows 18 by the spring element 21 shifted, so that a switching position of the valve 22 is reset again, the valve 22 is closed again, for example.
  • the hydraulic temperature compensator 5 thus serves to build up pressure in the valve 1.
  • the pressure of the hydraulic fluid H will increase slowly due to a temperature expansion.
  • 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 a compensation volume for compensation of a temperature-related volume expansion of the hydraulic fluid H.
  • a volume change produced due to slow processes for example a temperature change
  • the throttle point 24 is practically permeable to the hydraulic fluid H during slow processes
  • the limitation of the pressure increase of the hydraulic fluid H will also be effective for the other filled with the hydraulic fluid H areas of the valve 1, namely for example for the first sub-chamber 10 and the metal bellows 18. This in turn allows a position, in particular rest position of the secondary plunger 20 are kept virtually independent of temperature fluctuations on the valve, whereby a switching accuracy is improved.
  • Fig.2 shows a sectional side view of a hydraulic temperature compensator 25 according to a second Embodiment which, for example, instead of the hydraulic temperature compensator 5 in the valve 1 can be installed.
  • the hydraulic temperature compensator 25 has opposite the hydraulic temperature compensator 5 an additional compression spring 26 in the gas-filled chamber 12.
  • the 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 bottom 27 of the inner metal bellows 7.
  • the compression spring 26 causes the system pressure of the hydraulic fluid to increase.
  • a relationship between a pressure change of the hydraulic fluid H and an associated volume increase of the second sub-chamber 11 can be set very precisely, and thus also 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 is used for example in place of the hydraulic temperature compensator 5 in the valve 1.
  • the hydraulic temperature compensator 28 has a flutter valve 29 on the dividing wall, which has an associated flap 30 on an outer side of the dividing wall 8 which borders on the first partial chamber 10.
  • the flutter valve 29 causes a "dead time" between two actuations of the piezoelectric actuator 2 is reduced during normal operation. Because each time the piezoelectric actuator 2 presses the lid 9 down over the plunger 4, the pressure increases as described in the first sub-chamber 10.
  • the flutter valve 29 (or any other suitable unidirectional valve which has a comparatively large flow cross-section and allows the hydraulic fluid from the second sub-chamber 11 into the first Partkammmer 10) accelerates this pressure compensation and allows a faster re-actuation of the piezoelectric actuator 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 more integrated into the valve 1, for example, in that the outer metal bellows 6 and the metal bellows 18 are present as a single metal bellows and thus the actuator 20 would be separated from the second metal bellows 7 only by the hydraulic fluid H.
  • the hydraulic line 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)

Claims (3)

  1. Dispositif de transmission de course (1), comprenant au moins
    - un compensateur de température hydraulique (5; 25; 28), le compensateur de température hydraulique (5; 25; 28) comportant 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 seconde chambre partielle (11) qui sont reliées hydrauliquement l'une à l'autre par au moins un étranglement (24),
    - la seconde chambre partielle (11) étant contiguë à la chambre remplie de gaz (12)
    et le dispositif de transmission de course (1) comprenant, en outre :
    - un actionneur de course (2) agissant sur le compensateur de température (5; 25; 28) 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; 25; 28),
    - l'autre chambre hydraulique (18a) étant en communication fluidique avec un élément de réglage (20) monté mobile en translation.
  2. Dispositif de transmission de course (1) selon la revendication 1, l'actionneur de course (2) et le compensateur de température (5; 25; 28) étant maintenus entre deux paliers fixes (3, 14).
  3. Dispositif de transmission de course (1) selon l'une des revendications 1 à 2, le dispositif de transmission de course (1) représentant une partie d'un injecteur.
EP15001834.9A 2010-09-13 2011-08-22 Dispositif hydraulique de transmission de course avec un compensateur de température hydraulique Active EP2947308B1 (fr)

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
EP11749802.2A EP2616665B1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP11749802.2A Division-Into EP2616665B1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique
EP11749802.2A Division EP2616665B1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique

Publications (2)

Publication Number Publication Date
EP2947308A1 EP2947308A1 (fr) 2015-11-25
EP2947308B1 true EP2947308B1 (fr) 2017-09-27

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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
EP11749802.2A Active EP2616665B1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique

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EP11749802.2A Active EP2616665B1 (fr) 2010-09-13 2011-08-22 Compensateur de température hydraulique et élément de transmission de course hydraulique

Country Status (6)

Country Link
US (1) US9488194B2 (fr)
EP (2) EP2947308B1 (fr)
DE (1) DE102010040612A1 (fr)
HU (1) HUE027360T2 (fr)
PL (1) PL2616665T3 (fr)
WO (1) WO2012034823A1 (fr)

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* Cited by examiner, † Cited by third party
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
US20220205463A1 (en) * 2019-04-17 2022-06-30 Metismotion Gmbh Hydraulic transmission unit for an actuator

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 Motorentechnik GmbH & Co. KG, 52078 Aachen 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
EP1591656B1 (fr) * 2004-04-26 2008-03-12 Isuzu Motors Limited Méchanisme d'absortion de l'expansion différentielle et une soupape d'injection de combustible comprenant celui-ci
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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EP2616665B1 (fr) 2016-01-20
US9488194B2 (en) 2016-11-08
WO2012034823A1 (fr) 2012-03-22
DE102010040612A1 (de) 2012-03-15
EP2616665A1 (fr) 2013-07-24
HUE027360T2 (en) 2016-09-28
PL2616665T3 (pl) 2016-07-29
EP2947308A1 (fr) 2015-11-25
US20130269790A1 (en) 2013-10-17

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