EP3724501B1 - Fuel delivery device for cryogenic fuels - Google Patents

Fuel delivery device for cryogenic fuels Download PDF

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Publication number
EP3724501B1
EP3724501B1 EP18800579.7A EP18800579A EP3724501B1 EP 3724501 B1 EP3724501 B1 EP 3724501B1 EP 18800579 A EP18800579 A EP 18800579A EP 3724501 B1 EP3724501 B1 EP 3724501B1
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EP
European Patent Office
Prior art keywords
delivery device
pump piston
fuel delivery
hollow cylinder
pressure chamber
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EP18800579.7A
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German (de)
French (fr)
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EP3724501A1 (en
Inventor
Dirk SCHNITTGER
Friedrich Howey
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3724501A1 publication Critical patent/EP3724501A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • 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
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0245—High pressure fuel supply systems; Rails; Pumps; Arrangement of valves
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/105—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor
    • F04B9/1053—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber reciprocating movement of the pumping member being obtained by a double-acting liquid motor one side of the double-acting liquid motor being always under the influence of the liquid under pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
    • F04B15/08—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure the liquids having low boiling points
    • F04B2015/081—Liquefied gases

Definitions

  • a pressure equalization is effected, which leads to the formation of a hydraulic stop that limits the working stroke of the pump piston.
  • the hydraulic stop prevents mechanical impact, so that the load on the pump piston is further reduced. This means that the wear on the pump piston is further reduced and the service life of the piston pump is further increased. Furthermore, the hydraulic stop reduces the noise generated during operation of the piston pump.
  • the upper end position of the pump piston is also specified via the hydraulic stop.
  • the position of the connecting channel in relation to the pump piston is therefore to be selected in such a way that the pump piston releases the connecting channel shortly before reaching the upper end position.
  • the pressure equalization that then occurs leads to the formation of the hydraulic stop which limits the working stroke of the pump piston.
  • a check valve is preferably arranged, which prevents the hydraulic pressure medium from flowing back from the storage volume into the first pressure chamber. This means that the connection channel can only be flown through in one direction, namely from the first pressure chamber in the direction of the storage volume or the further pressure chamber. This ensures that the hydraulic pressure required for resetting the pump piston can be built up in the storage volume and the further pressure chamber.
  • the storage volume can be connected to a leakage line via a pressure limiting valve.
  • a pressure limiting valve With the aid of the pressure relief valve, a maximum hydraulic pressure can be set in the storage volume and in the further pressure chamber. Since the maximum pressure in the storage volume and in the further pressure chamber depends on the design of the hydraulic stop, this can also be used to influence the upper end position of the pump piston.
  • a pressure relief valve is not necessary if the storage volume can be relieved in some other way.
  • the storage volume can be connected to a low-pressure space via at least one relief channel formed in the hollow cylinder or via at least one relief opening formed in the storage sleeve.
  • the relief opening in the storage sleeve can be designed, for example, as a simple radial bore, so that this embodiment can be implemented in a particularly simple manner.
  • the storage sleeve preferably has a plurality of relief openings, which are furthermore preferably arranged at the same angular distance from one another.
  • the at least one relief opening formed in the storage sleeve is preferably closed.
  • the relief opening is only released when the storage sleeve has a predetermined stroke relative to the hollow cylinder, so that hydraulic pressure medium can flow out of the storage volume into the low-pressure space.
  • the resulting pressure equalization between the storage volume and the low-pressure space causes a hydraulic limitation of the stroke of the storage sleeve before it reaches a mechanical stop. In this way, wear on the storage sleeve can be reduced. At the same time, the noise emissions can be further reduced.
  • At least one relief channel is provided in the hollow cylinder instead of the at least one relief opening in the storage sleeve, the mode of operation is essentially the same. This means that the relief channel is only released when the storage sleeve has reached a predetermined position.
  • the storage volume can be connected to a low-pressure space via an annular gap between the hollow cylinder and the storage sleeve.
  • the annular gap creates a circumferential opening of the storage volume to the low-pressure space, so that neither a relief opening in the storage sleeve nor a relief channel is required in the hollow cylinder. This enables a rotationally symmetrical design of at least the storage sleeve, so that its manufacture is simplified.
  • the circumferential annular gap also ensures that the hydraulic pressure medium flows off quickly and evenly from the storage volume into the low-pressure space.
  • the low-pressure space is advantageously connected to a tank for the hydraulic pressure medium via a return line and / or via the leakage line.
  • the amount of hydraulic pressure medium supplied to the low-pressure chamber is therefore not lost to the system.
  • the hydraulic pressure medium can be, for example, an oil, in particular an engine oil.
  • the hollow cylinder preferably has a stepped outer contour with an annular shoulder.
  • the dimensions of the storage volume in the radial direction can be specified via the width of the shoulder.
  • the storage sleeve delimiting the storage volume is arranged on the outer diameter of the hollow cylinder.
  • the annular shoulder of the hollow cylinder merges into a guide surface for the storage sleeve via a cone. If the overlap of the storage sleeve with the guide surface for opening the storage volume is briefly abandoned via a circumferential annular gap, the cone facilitates the return of the storage sleeve or the re-immersion of the hollow cylinder in the storage sleeve.
  • the storage sleeve have a stepped inner contour to limit the storage volume.
  • the storage sleeve also preferably forms an annular shoulder, which furthermore preferably lies opposite the annular shoulder of the hollow cylinder on the storage volume, the distance between the two annular shoulders being variable by a stroke movement of the storage sleeve relative to the hollow cylinder.
  • the storage sleeve Due to the stepped inner contour, the storage sleeve has two different guide diameters. In the area of the larger guide diameter, via which the storage volume is limited in the radial direction, the inner contour of the storage sleeve preferably merges at the end via a cone into an end face. The cone in turn has the task of making it easier to re-immerse the hollow cylinder in the storage sleeve.
  • the pump piston 2 When the pump piston 2 has reached its upper end position (see Fig. 2 ), it releases a connecting channel 11 in which a check valve 12 is arranged, which enables an inflow of hydraulic pressure medium into the storage volume 8 and into the second pressure chamber 7. In this way, pressure equalization is achieved in the two pressure chambers 5, 7, which leads to the formation of a hydraulic stop. This means that the working stroke of the pump piston 2 is limited hydraulically, as a result of which the wear on the pump piston 2 is reduced.
  • the cone 22 of the hollow cylinder 4 connects the shoulder 21 with the guide surface 23 and the cone 25 of the storage sleeve 9 ends at an end face 26.
  • the annular gap 18 ensures a uniform outflow of the hydraulic pressure medium from the storage volume 8 into the low-pressure chamber 17.
  • the embodiments without pressure relief valve 13 have in common that the return spring 10 resets the storage sleeve 9 until the connection between the storage volume 8 and the low-pressure chamber 17 via the relief openings 16, the relief channel 15 or the annular gap 18 is closed again.
  • the construction is designed in such a way that the volume present at this point in time is sufficient to bring about the return of the pump piston 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft eine Kraftstofffördereinrichtung für kryogene Kraftstoffe mit den Merkmalen des Oberbegriffs des Anspruchs 1.The invention relates to a fuel delivery device for cryogenic fuels with the features of the preamble of claim 1.

Bei dem kryogenen Kraftstoff kann es sich insbesondere um Erdgas ("Natural Gas" = NG) handeln, das beispielsweise an Bord eines Kraftfahrzeugs zum Betreiben einer Brennkraftmaschine in flüssiger Form ("Liquefied Natural Gas" = LNG) in einem speziell dafür ausgelegten Tank bevorratet wird.The cryogenic fuel can in particular be natural gas ("Natural Gas" = NG), which is stored in liquid form ("Liquefied Natural Gas" = LNG) in a specially designed tank, for example, on board a motor vehicle to operate an internal combustion engine .

Stand der TechnikState of the art

Aus der EP 2 541 062 A1 ist eine Kolbenpumpe für kryogene Kraftstoffe, insbesondere für Erdgas, mit einem hin- und herbeweglichen Pumpenkolben bekannt. Der Pumpenkolben begrenzt einen Pumpenarbeitsraum, der mit flüssigem Erdgas befüllbar ist, so dass im Pumpenarbeitsraum vorhandenes flüssiges Erdgas über eine Hubbewegung des Pumpenkolbens mit Hochdruck beaufschlagbar ist. Andernends begrenzt der Pumpenkolben einen Kopplerraum, der mit einem hydraulischen Druckmittel befüllbar ist, um den Pumpenkolben in einer Hubbewegung anzutreiben. Alternativ wird ein elektrischer, pneumatischer oder mechanischer Antrieb vorgeschlagen. Eine weitere Kraftstofffördereinrichtung für kryogene Kraftstoffe ist aus dem Dokument US 7 293 418 B2 bekannt.From the EP 2 541 062 A1 a piston pump for cryogenic fuels, in particular for natural gas, with a reciprocating pump piston is known. The pump piston delimits a pump working space which can be filled with liquid natural gas, so that liquid natural gas present in the pump working space can be acted upon with high pressure via a stroke movement of the pump piston. At the other end, the pump piston delimits a coupler space which can be filled with a hydraulic pressure medium in order to drive the pump piston in a lifting movement. Alternatively, an electrical, pneumatic or mechanical drive is proposed. Another fuel delivery device for cryogenic fuels is from the document US 7 293 418 B2 known.

Die meisten Kolbenpumpen, und zwar unabhängig von der jeweiligen Antriebsart, weisen eine Schraubendruckfeder zur Rückstellung des Pumpenkolbens auf. Die Schraubendruckfeder ist in der Regel am Pumpenkolben abgestützt, so dass auf den Pumpenkolben zusätzlich Torsions- und Querkräfte wirken. Insbesondere die Querkräfte führen zu einem erhöhten Verschleiß im Bereich der Führungen und/oder Dichtungen am Pumpenkolben, was sich wiederum negativ auf die Lebensdauer der Kolbenpumpe auswirkt.Most piston pumps, regardless of the type of drive, have a helical compression spring to reset the pump piston. The helical compression spring is usually supported on the pump piston, so that additional torsional and transverse forces act on the pump piston. In particular, the transverse forces lead to increased wear in the area of the guides and / or seals on the pump piston, which in turn has a negative effect on the service life of the piston pump.

Aufgabe der vorliegenden Erfindung ist es, eine Kraftstofffördereinrichtung für kryogene Kraftstoffe mit einer Kolbenpumpe anzugeben, deren Lebensdauer gesteigert ist. Insbesondere soll der Verschleiß im Bereich von Führungen und/oder Dichtungen eines hin- und herbeweglichen Pumpenkolbens der Kolbenpumpe gemindert werden.The object of the present invention is to specify a fuel delivery device for cryogenic fuels with a piston pump, the service life of which is increased. In particular, wear in the area of guides and / or seals of a reciprocating pump piston of the piston pump should be reduced.

Zur Lösung der Aufgabe wird die Kraftstofffördereinrichtung mit den Merkmalen des Anspruchs 1 vorgeschlagen. Vorteilhafte Weiterbildungen der Erfindung sind den Unteransprüchen zu entnehmen.To achieve the object, the fuel delivery device with the features of claim 1 is proposed. Advantageous further developments of the invention can be found in the subclaims.

Offenbarung der ErfindungDisclosure of the invention

Die vorgeschlagene Kraftstofffördereinrichtung für kryogene Kraftstoffe umfasst eine Kolbenpumpe zur Förderung des kryogenen Kraftstoffs auf Hochdruck, wobei die Kolbenpumpe einen hin- und herbeweglichen Pumpenkolben aufweist, der einenends einen Kompressionsraum und andernends einen in einem Hohlzylinder ausgebildeten Druckraum begrenzt, der mit einem hydraulischen Druckmittel beaufschlagbar ist. Erfindungsgemäß weist der Pumpenkolben einen ringförmigen Absatz zur Begrenzung eines im Hohlzylinder ausgebildeten weiteren Druckraums auf, der zur Rückstellung des Pumpenkolbens ebenfalls mit dem hydraulischen Druckmittel beaufschlagbar ist. Der weitere Druckraum ist dabei mit einem Speichervolumen gekoppelt, das durch eine Speicherhülse begrenzt wird, die auf dem Hohlzylinder hin- und herbeweglich angeordnet und mittels einer Rückstellfeder vorgespannt ist.The proposed fuel delivery device for cryogenic fuels comprises a piston pump for delivering the cryogenic fuel to high pressure, the piston pump having a reciprocating pump piston that delimits a compression chamber at one end and a pressure chamber formed in a hollow cylinder at the other end, which can be acted upon by a hydraulic pressure medium. According to the invention, the pump piston has an annular shoulder to delimit a further pressure chamber formed in the hollow cylinder, which can also be acted upon by the hydraulic pressure medium in order to reset the pump piston. The further pressure chamber is coupled to a storage volume which is delimited by a storage sleeve which is arranged to be movable to and fro on the hollow cylinder and is pretensioned by means of a return spring.

Der Pumpenkolben der Kolbenpumpe der erfindungsgemäßen Kraftstofffördereinrichtung ist demnach hydraulisch antreibbar. Bei einer Beaufschlagung des ersten bzw. endseitig in Bezug auf den Pumpenkolben angeordneten Druckraums mit dem hydraulischen Druckmittel bewegt sich der Pumpenkolben in Richtung des Kompressionsraums, das heißt in Richtung einer oberen Endlage, in der das Volumen des Kompressionsraums minimal ist. Der Pumpenkolben führt in diesem Fall einen Arbeitshub aus, bei dem im Kompressionsraum vorhandener Kraftstoff verdichtet wird.The pump piston of the piston pump of the fuel delivery device according to the invention can accordingly be driven hydraulically. When the hydraulic pressure medium is applied to the first or end-side pressure chamber with respect to the pump piston, the pump piston moves in the direction of the compression chamber, that is, in the direction of an upper end position in which the volume of the compression chamber is minimal. In this case, the pump piston performs a working stroke in which the fuel present in the compression chamber is compressed.

Die Rückstellung des Pumpenkolbens wird ebenfalls hydraulisch bewirkt, und zwar über den hydraulischen Druck im weiteren Druckraum. Mit zunehmendem Arbeitshub des Pumpenkolbens verringert sich das Volumen des weiteren Druckraums, wobei die Volumenverringerung des weiteren Druckraums durch eine Volumenvergrößerung des Speichervolumens kompensiert wird. Die das Speichervolumen begrenzende Speicherhülse bewegt sich dabei in Richtung der Rückstellfeder, so dass diese gespannt wird. Entsprechend steigt die auf die Speicherhülse wirkende Vorspannkraft. Hat der Pumpenkolben seine obere Endlage erreicht, ist die Vorspannkraft maximal. Die Vorspannkraft führt schließlich zur Rückstellung der Speicherhülse, wobei der Druck im Speichervolumen und im weiteren Druckraum ansteigt und zur Rückstellung des Pumpenkolbens führt.The resetting of the pump piston is also effected hydraulically, via the hydraulic pressure in the further pressure chamber. As the working stroke of the pump piston increases, the volume of the further pressure chamber decreases, the reduction in volume of the further pressure chamber being compensated for by an increase in the volume of the storage volume. The storage sleeve delimiting the storage volume moves in the direction of the return spring so that it is tensioned. The prestressing force acting on the storage sleeve increases accordingly. When the pump piston has reached its upper end position, the pre-tensioning force is maximum. The pretensioning force finally leads to the resetting of the storage sleeve, the pressure in the storage volume and in the further pressure chamber increasing and leading to resetting of the pump piston.

Da die Bewegungen des Pumpenkolbens allein über die am Pumpenkolben anliegenden hydraulischen Druckverhältnisse gesteuert werden, wirken auf den Pumpenkolben keine Torsions- oder Querkräfte, welche die am Pumpenkolben ausgebildeten Führungen und/oder Dichtungen belasten könnten. Das heißt, dass die Führungen und/oder Dichtungen einem geringeren Verschleiß ausgesetzt sind. Entsprechend werden auf diese Weise die Robustheit und die Lebensdauer der Kolbenpumpe bzw. der Kraftstofffördereinrichtung gesteigert.Since the movements of the pump piston are controlled solely via the hydraulic pressure conditions applied to the pump piston, no torsional or transverse forces act on the pump piston, which could load the guides and / or seals formed on the pump piston. This means that the guides and / or seals are exposed to less wear. In this way, the robustness and the service life of the piston pump or the fuel delivery device are increased accordingly.

Zwar weist auch die Kolbenpumpe der erfindungsgemäßen Kraftstofffördereinrichtung eine Rückstellfeder auf, diese ist jedoch nicht unmittelbar am Pumpenkolben, sondern an der außen auf dem Hohlzylinder angeordneten Speicherhülse abgestützt. Die Speicherhülse und der Hohlzylinder nehmen somit die Torsions- und Querkräfte der Rückstellfeder auf. Der Pumpenkolben bleibt unbelastet.Although the piston pump of the fuel delivery device according to the invention also has a return spring, this is not supported directly on the pump piston, but on the storage sleeve arranged on the outside of the hollow cylinder. The storage sleeve and the hollow cylinder thus absorb the torsional and transverse forces of the return spring. The pump piston remains unloaded.

Die Abstützung der Rückstellfeder an der Speicherhülse besitzt zudem den Vorteil, dass aufgrund des verfügbaren Durchmessers eine besonders große und damit kräftige Feder einsetzbar ist. Darüber hinaus kann die Rückstellfeder einfach integriert werden.The support of the return spring on the storage sleeve also has the advantage that a particularly large and therefore powerful spring can be used due to the available diameter. In addition, the return spring can be easily integrated.

Gemäß einer bevorzugten Ausführungsform der Erfindung ist das Speichervolumen in Abhängigkeit von der Lage des Pumpenkolbens, vorzugsweise in einer oberen Endlage des Pumpenkolbens, über einen im Hohlzylinder ausgebildeten Verbindungskanal mit dem ersten Druckraum hydraulisch verbindbar. Über die hydraulische Verbindung mit dem ersten Druckraum ist die Befüllung des Speichervolumens und damit des weiteren Druckraums mit dem hydraulischen Druckmittel sichergestellt. Das heißt, dass nur ein Anschluss für das hydraulische Druckmittel erforderlich ist.According to a preferred embodiment of the invention, the storage volume is dependent on the position of the pump piston, preferably in an upper end position of the pump piston, via a connecting channel formed in the hollow cylinder hydraulically connectable to the first pressure chamber. The hydraulic connection with the first pressure chamber ensures that the storage volume and thus the further pressure chamber are filled with the hydraulic pressure medium. This means that only one connection is required for the hydraulic pressure medium.

Ist eine hydraulische Verbindung des Speichervolumens - und damit des weiteren Druckraums - mit dem ersten Druckraum hergestellt, wird ein Druckausgleich bewirkt, der zur Ausbildung eines den Arbeitshub des Pumpenkolbens begrenzenden hydraulischen Anschlags führt. Der hydraulische Anschlag verhindert ein mechanisches Anschlagen, so dass die Belastung des Pumpenkolbens weiter gesenkt wird. Das heißt, dass der Verschleiß am Pumpenkolben weiter verringert bzw. die Lebensdauer der Kolbenpumpe weiter gesteigert wird. Ferner wird durch den hydraulischen Anschlag die Geräuschentwicklung im Betrieb der Kolbenpumpe gesenkt.If a hydraulic connection of the storage volume - and thus of the further pressure chamber - is established with the first pressure chamber, a pressure equalization is effected, which leads to the formation of a hydraulic stop that limits the working stroke of the pump piston. The hydraulic stop prevents mechanical impact, so that the load on the pump piston is further reduced. This means that the wear on the pump piston is further reduced and the service life of the piston pump is further increased. Furthermore, the hydraulic stop reduces the noise generated during operation of the piston pump.

Über den hydraulischen Anschlag ist zugleich die obere Endlage des Pumpenkolbens vorgegeben. Die Lage des Verbindungskanals in Bezug auf den Pumpenkolben ist daher derart zu wählen, dass der Pumpenkolben kurz vor Erreichen der oberen Endlage den Verbindungskanal freigibt. Der sich dann einstellende Druckausgleich führt zur Ausbildung des hydraulischen Anschlags, der den Arbeitshub des Pumpenkolbens begrenzt.The upper end position of the pump piston is also specified via the hydraulic stop. The position of the connecting channel in relation to the pump piston is therefore to be selected in such a way that the pump piston releases the connecting channel shortly before reaching the upper end position. The pressure equalization that then occurs leads to the formation of the hydraulic stop which limits the working stroke of the pump piston.

Im Verbindungskanal ist vorzugsweise ein Rückschlagventil angeordnet, das ein Rückströmen des hydraulischen Druckmittels aus dem Speichervolumen in den ersten Druckraum verhindert. Das heißt, dass der Verbindungskanal nur in einer Richtung und zwar vom ersten Druckraum in Richtung des Speichervolumens bzw. des weiteren Druckraums durchströmt werden kann. Dadurch ist sichergestellt, dass im Speichervolumen und dem weiteren Druckraum der für die Rückstellung des Pumpenkolbens erforderliche hydraulische Druck aufgebaut werden kann.In the connecting channel, a check valve is preferably arranged, which prevents the hydraulic pressure medium from flowing back from the storage volume into the first pressure chamber. This means that the connection channel can only be flown through in one direction, namely from the first pressure chamber in the direction of the storage volume or the further pressure chamber. This ensures that the hydraulic pressure required for resetting the pump piston can be built up in the storage volume and the further pressure chamber.

Des Weiteren wird vorgeschlagen, dass das Speichervolumen über ein Druckbegrenzungsventil mit einer Leckageleitung verbindbar ist. Mit Hilfe des Druckbegrenzungsventils kann ein maximaler hydraulischer Druck im Speichervolumen und im weiteren Druckraum eingestellt werden. Da vom maximalen Druck im Speichervolumen und im weiteren Druckraum die Ausbildung des hydraulischen Anschlags abhängt, kann hierüber zugleich Einfluss auf die obere Endlage des Pumpenkolbens genommen werden.It is also proposed that the storage volume can be connected to a leakage line via a pressure limiting valve. With the aid of the pressure relief valve, a maximum hydraulic pressure can be set in the storage volume and in the further pressure chamber. Since the maximum pressure in the storage volume and in the further pressure chamber depends on the design of the hydraulic stop, this can also be used to influence the upper end position of the pump piston.

Ein Druckbegrenzungsventil ist entbehrlich, wenn auf andere Art eine Entlastung des Speichervolumens bewirkt werden kann. Gemäß einer weiteren bevorzugten Ausführungsform ist daher das Speichervolumen in Abhängigkeit von der Lage der Speicherhülse über mindestens einen im Hohlzylinder ausgebildeten Entlastungkanal oder über mindestens eine in der Speicherhülse ausgebildete Entlastungsöffnung mit einem Niederdruckraum verbindbar. Die Entlastungsöffnung in der Speicherhülse kann beispielsweise als einfache Radialbohrung ausgeführt sein, so dass diese Ausführungsform besonders einfach umgesetzt werden kann. Bevorzugt weist die Speicherhülse mehrere Entlastungsöffnungen auf, die weiterhin bevorzugt in gleichem Winkelabstand zueinander angeordnet sind.A pressure relief valve is not necessary if the storage volume can be relieved in some other way. According to a further preferred embodiment, depending on the position of the storage sleeve, the storage volume can be connected to a low-pressure space via at least one relief channel formed in the hollow cylinder or via at least one relief opening formed in the storage sleeve. The relief opening in the storage sleeve can be designed, for example, as a simple radial bore, so that this embodiment can be implemented in a particularly simple manner. The storage sleeve preferably has a plurality of relief openings, which are furthermore preferably arranged at the same angular distance from one another.

Während des Arbeitshubs des Pumpenkolbens ist vorzugsweise die mindestens eine in der Speicherhülse ausgebildete Entlastungsöffnung verschlossen. Erst bei einem vorgegebenen Hub der Speicherhülse gegenüber dem Hohlzylinder wird die Entlastungsöffnung freigegeben, so dass hydraulisches Druckmittel aus dem Speichervolumen in den Niederdruckraum abfließen kann. Der sich dabei einstellende Druckausgleich zwischen dem Speichervolumen und dem Niederdruckraum bewirkt eine hydraulische Begrenzung des Hubs der Speicherhülse bevor diese einen mechanischen Anschlag erreicht. Auf diese Weise kann der Verschleiß an der Speicherhülse gemindert werden. Zugleich können die Geräuschemissionen weiter verringert werden.During the working stroke of the pump piston, the at least one relief opening formed in the storage sleeve is preferably closed. The relief opening is only released when the storage sleeve has a predetermined stroke relative to the hollow cylinder, so that hydraulic pressure medium can flow out of the storage volume into the low-pressure space. The resulting pressure equalization between the storage volume and the low-pressure space causes a hydraulic limitation of the stroke of the storage sleeve before it reaches a mechanical stop. In this way, wear on the storage sleeve can be reduced. At the same time, the noise emissions can be further reduced.

Sofern anstelle der mindestens einen Entlastungsöffnung in der Speicherhülse mindestens ein Entlastungskanal im Hohlzylinder vorgesehen ist, ist die Funktionsweise im Wesentlichen die gleiche. Das heißt, dass der Entlastungskanal erst freigegeben wird, wenn die Speicherhülse eine vorgegebene Position erreicht hat.If at least one relief channel is provided in the hollow cylinder instead of the at least one relief opening in the storage sleeve, the mode of operation is essentially the same. This means that the relief channel is only released when the storage sleeve has reached a predetermined position.

Gemäß einer weiteren bevorzugten Ausführungsform der Erfindung ist das Speichervolumen in Abhängigkeit von der Lage der Speicherhülse über einen Ringspalt zwischen dem Hohlzylinder und der Speicherhülse mit einem Niederdruckraum verbindbar. Der Ringspalt schafft eine umlaufende Öffnung des Speichervolumens zum Niederdruckraum, so dass weder eine Entlastungsöffnung in der Speicherhülse, noch ein Entlastungskanal im Hohlzylinder erforderlich ist. Dies ermöglicht eine rotationssymmetrische Ausbildung zumindest der Speicherhülse, so dass deren Herstellung vereinfacht wird. Der umlaufende Ringspalt gewährleistet zudem ein gleichmäßiges und schnelles Abfließen des hydraulischen Druckmittels aus dem Speichervolumen in den Niederdruckraum.According to a further preferred embodiment of the invention, depending on the position of the storage sleeve, the storage volume can be connected to a low-pressure space via an annular gap between the hollow cylinder and the storage sleeve. The annular gap creates a circumferential opening of the storage volume to the low-pressure space, so that neither a relief opening in the storage sleeve nor a relief channel is required in the hollow cylinder. This enables a rotationally symmetrical design of at least the storage sleeve, so that its manufacture is simplified. The circumferential annular gap also ensures that the hydraulic pressure medium flows off quickly and evenly from the storage volume into the low-pressure space.

Vorteilhafterweise ist der Niederdruckraum über eine Rücklaufleitung und/oder über die Leckageleitung mit einen Tank für das hydraulische Druckmittel verbunden. Die dem Niederdruckraum zugeführte Menge des hydraulischen Druckmittels geht somit dem System nicht verloren. Bei dem hydraulischen Druckmittel kann es sich beispielsweise um ein Öl, insbesondere um ein Motoröl, handeln.The low-pressure space is advantageously connected to a tank for the hydraulic pressure medium via a return line and / or via the leakage line. The amount of hydraulic pressure medium supplied to the low-pressure chamber is therefore not lost to the system. The hydraulic pressure medium can be, for example, an oil, in particular an engine oil.

Zur Ausbildung des Speichervolumens weist vorzugsweise der Hohlzylinder eine gestufte Außenkontur mit einem ringförmigen Absatz auf. Über die Breite des Absatzes kann die Abmessung des Speichervolumens in radialer Richtung vorgegeben werden. Die das Speichervolumen begrenzende Speicherhülse ist hierzu auf dem außenliegenden Durchmesser des Hohlzylinders angeordnet. In Weiterbildung der Erfindung wird vorgeschlagen, dass der ringförmige Absatz des Hohlzylinders über einen Konus in eine Führungsfläche für die Speicherhülse übergeht. Wird die Überdeckung der Speicherhülse mit der Führungsfläche zum Öffnen des Speichervolumens über einen umlaufenden Ringspalt kurzzeitig aufgegeben, erleichtert der Konus die Rückstellung der Speicherhülse bzw. das Wiedereintauchen des Hohlzylinders in die Speicherhülse.To form the storage volume, the hollow cylinder preferably has a stepped outer contour with an annular shoulder. The dimensions of the storage volume in the radial direction can be specified via the width of the shoulder. For this purpose, the storage sleeve delimiting the storage volume is arranged on the outer diameter of the hollow cylinder. In a further development of the invention, it is proposed that the annular shoulder of the hollow cylinder merges into a guide surface for the storage sleeve via a cone. If the overlap of the storage sleeve with the guide surface for opening the storage volume is briefly abandoned via a circumferential annular gap, the cone facilitates the return of the storage sleeve or the re-immersion of the hollow cylinder in the storage sleeve.

Alternativ oder ergänzend wird vorgeschlagen, dass die Speicherhülse zur Begrenzung des Speichervolumens eine gestufte Innenkontur aufweist. Das heißt, dass auch die Speicherhülse bevorzugt einen ringförmigen Absatz ausbildet, der weiterhin bevorzugt dem ringförmigen Absatz des Hohlzylinders am Speichervolumen gegenüber liegt, wobei der Abstand zwischen den beiden ringförmigen Absätze durch eine Hubbewegung der Speicherhülse gegenüber dem Hohlzylinder veränderbar ist. Aufgrund der gestuften Innenkontur weist die Speicherhülse zwei unterschiedliche Führungsdurchmesser auf. Im Bereich des größeren Führungsdurchmessers, über den das Speichervolumen in radialer Richtung begrenzt wird, geht vorzugsweise die Innenkontur der Speicherhülse endseitig über einen Konus in eine Stirnfläche über. Der Konus hat wiederum die Aufgabe, das Wiedereintauchen des Hohlzylinders in die Speicherhülse zu erleichtern.As an alternative or in addition, it is proposed that the storage sleeve have a stepped inner contour to limit the storage volume. This means that the storage sleeve also preferably forms an annular shoulder, which furthermore preferably lies opposite the annular shoulder of the hollow cylinder on the storage volume, the distance between the two annular shoulders being variable by a stroke movement of the storage sleeve relative to the hollow cylinder. Due to the stepped inner contour, the storage sleeve has two different guide diameters. In the area of the larger guide diameter, via which the storage volume is limited in the radial direction, the inner contour of the storage sleeve preferably merges at the end via a cone into an end face. The cone in turn has the task of making it easier to re-immerse the hollow cylinder in the storage sleeve.

Das Speichervolumen wird demnach bevorzugt durch einen Ringraum gebildet, der konzentrisch in Bezug auf den Pumpenkolben bzw. den ersten Druckraum zwischen dem Hohlzylinder und der Speicherhülse angeordnet ist. Der mit dem Speichervolumen gekoppelte weitere Druckraum wird vorzugsweise ebenfalls durch einen Ringraum gebildet, der zwischen dem Pumpenkolben und dem Hohlzylinder angeordnet ist.The storage volume is accordingly preferably formed by an annular space which is arranged concentrically with respect to the pump piston or the first pressure space between the hollow cylinder and the storage sleeve. The further pressure space coupled to the storage volume is preferably also formed by an annular space which is arranged between the pump piston and the hollow cylinder.

Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der beigefügten Zeichnungen näher erläutert. Diese zeigen:

  • Fig. 1 einen schematischen Längsschnitt durch eine Kolbenpumpe einer erfindungsgemäßen Kraftstofffördereinrichtung gemäß einer ersten bevorzugten Ausführungsform,
  • Fig. 2 einen vergrößerten Ausschnitt der Fig. 1 im Bereich des hydraulischen Antriebs am Ende eines Arbeitshubs des Pumpenkolbens,
  • Fig. 3 den Ausschnitt der Fig. 2 während eines Saughubs des Pumpenkolbens,
  • Fig. 4 einen schematischen Längsschnitt durch eine Kolbenpumpe einer erfindungsgemäßen Kraftstofffördereinrichtung gemäß einer zweiten bevorzugten Ausführungsform, und zwar beschränkt auf den Bereich des hydraulischen Antriebs während eines Arbeitshubs des Pumpenkolbens,
  • Fig. 5 den Ausschnitt der Fig. 4 am Ende eines Arbeitshubs des Pumpenkolbens,
  • Fig. 6 einen schematischen Längsschnitt durch eine Kolbenpumpe einer erfindungsgemäßen Kraftstofffördereinrichtung gemäß einer dritten bevorzugten Ausführungsform, und zwar beschränkt auf den Bereich des hydraulischen Antriebs während eines Arbeitshubs des Pumpenkolbens
  • Fig. 7 den Ausschnitt der Fig. 6 am Ende des Arbeitshubs des Pumpenkolbens, und
  • Fig. 8 einen schematischen Längsschnitt durch eine Kolbenpumpe einer erfindungsgemäßen Kraftstofffördereinrichtung gemäß einer vierten bevorzugten Ausführungsform, und zwar beschränkt auf den Bereich des hydraulischen Antriebs am Ende eines Arbeitshubs des Pumpenkolbens.
Preferred embodiments of the invention are explained in more detail below with reference to the accompanying drawings. These show:
  • Fig. 1 a schematic longitudinal section through a piston pump of a fuel delivery device according to the invention according to a first preferred embodiment,
  • Fig. 2 an enlarged section of the Fig. 1 in the area of the hydraulic drive at the end of a working stroke of the pump piston,
  • Fig. 3 the section of the Fig. 2 during a suction stroke of the pump piston,
  • Fig. 4 a schematic longitudinal section through a piston pump of a fuel delivery device according to the invention according to a second preferred embodiment, limited to the area of the hydraulic drive during a working stroke of the pump piston,
  • Fig. 5 the section of the Fig. 4 at the end of a working stroke of the pump piston,
  • Fig. 6 a schematic longitudinal section through a piston pump of a fuel delivery device according to the invention according to a third preferred embodiment, limited to the area of the hydraulic drive during a working stroke of the pump piston
  • Fig. 7 the section of the Fig. 6 at the end of the working stroke of the pump piston, and
  • Fig. 8 a schematic longitudinal section through a piston pump of a fuel delivery device according to the invention according to a fourth preferred embodiment, limited to the area of the hydraulic drive at the end of a working stroke of the pump piston.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Die in der Fig. 1 dargestellte erfindungsgemäße Kraftstofffördereinrichtung dient der Versorgung einer Brennkraftmaschine (nicht dargestellt) eines Kraftfahrzeugs mit Kraftstoff, wobei es sich um einen kryogenen Kraftstoff, vorzugsweise um Erdgas, handelt. Die Kraftstofffördereinrichtung umfasst eine Kolbenpumpe 1 zur Förderung des Kraftstoffs auf Hochdruck.The one in the Fig. 1 The fuel delivery device according to the invention shown serves to supply an internal combustion engine (not shown) of a motor vehicle with fuel, which is a cryogenic fuel, preferably natural gas. The fuel delivery device comprises a piston pump 1 for delivering the fuel to high pressure.

Der Kraftstoff wird in flüssiger Form in einem Tank (nicht dargestellt) bevorratet. Über einen Zulauf 27 und ein Saugventil 30 gelangt der Kraftstoff in einen Kompressionsraum 3 der Kolbenpumpe 1, der von einem hin- und herbeweglichen Pumpenkolben 2 begrenzt wird. Während eines Arbeitshubs des Pumpenkolbens 2 wird der im Kompressionsraum 3 vorhandene Kraftstoff verdichtet und über einen Ablauf 28 einem Pufferspeicher (nicht dargestellt) zugeführt. Im Bereich des Ablaufs 28 ist ein Rückschlagventil 29 angeordnet, um während eines erneuten Saughubs des Pumpenkolbens 2 ein Rückströmen des Kraftstoffs in den Kompressionsraum 3 zu verhindern. Ferner ist eine Rücklaufleitung 31 zum Abführen einer Leckagemenge des kryogenen Kraftstoffs vorgesehen, die über die Dichtungen des Pumpenkolbens 2 aus dem Kompressionsraum 3 entweicht.The fuel is stored in liquid form in a tank (not shown). Via an inlet 27 and a suction valve 30, the fuel reaches a compression chamber 3 of the piston pump 1, which is delimited by a reciprocating pump piston 2. During a working stroke of the pump piston 2, the fuel present in the compression chamber 3 is compressed and fed to a buffer store (not shown) via an outlet 28. A check valve 29 is arranged in the area of the outlet 28 in order to prevent the fuel from flowing back into the compression chamber 3 during a renewed suction stroke of the pump piston 2. Furthermore, a return line 31 is provided for discharging a leakage amount of the cryogenic fuel which escapes from the compression chamber 3 via the seals of the pump piston 2.

Der Pumpenkolben 2 der dargestellten Kolbenpumpe 1 weist an seinem dem Kompressionsraum 3 abgewandten Ende einen Kolbenabschnitt mit einem vergrößerten Außendurchmesser auf, der in einem Hohlzylinder 4 aufgenommen ist. Innerhalb des Hohlzylinders 4 begrenzt der Pumpenkolben 2 zwei Druckräume 5, 7, die mit einem hydraulischen Druckmittel beaufschlagbar sind. Bei Beaufschlagung des ersten Druckraums 5 mit dem hydraulischen Druckmittel führt der Pumpenkolben 2 einen Arbeitshub aus, da der erste Druckraum 5 endseitig in Bezug auf den Pumpenkolben 2 angeordnet ist. Der zweite Druckraum 7 wird durch einen am Pumpenkolben 2 ausgebildeten ringförmigen Absatz 6 begrenzt, der sich aufgrund des Durchmesserversprungs des Pumpenkolbens 2 ergibt. Das heißt, dass der zweite Druckraum 7 als Ringraum ausgebildet ist. Der zweite Druckraum 7 dient der Rückstellung des Pumpenkolbens 2, so dass dieser einen Saughub ausführt, während dessen der Kompressionsraum 3 erneut mit Kraftstoff befüllt wird.At its end facing away from the compression chamber 3, the pump piston 2 of the illustrated piston pump 1 has a piston section with an enlarged outer diameter, which is received in a hollow cylinder 4. Within the hollow cylinder 4, the pump piston 2 delimits two pressure chambers 5, 7, which can be acted upon by a hydraulic pressure medium. When the hydraulic pressure medium is applied to the first pressure chamber 5, the pump piston 2 executes a working stroke, since the first pressure chamber 5 is arranged at the end with respect to the pump piston 2. The second pressure chamber 7 is delimited by an annular shoulder 6 formed on the pump piston 2, which is due to the offset in diameter of the pump piston 2 results. This means that the second pressure chamber 7 is designed as an annular chamber. The second pressure chamber 7 serves to reset the pump piston 2 so that it executes a suction stroke, during which the compression chamber 3 is again filled with fuel.

Um die Rückstellung des Pumpenkolbens 2 zu bewirken, ist der zweite Druckraum 7 mit einem Speichervolumen 8 gekoppelt, das ebenfalls als Ringraum ausgebildet ist und durch den Hohlzylinder 4 und eine auf dem Hohlzylinder 4 hubbeweglich geführte Speicherhülse 9 begrenzt wird. Der Hohlzylinder 4 weist hierzu eine Außenkontur 20 mit einem ringförmigen Absatz 21 auf, der in eine Führungsfläche 23 für die Speicherhülse 9 übergeht. Die Speicherhülse 9 wiederum weist eine gestufte Innenkontur 24 zur Begrenzung des Speichervolumens 8 auf. Zudem wird die Speicherhülse in Richtung des Absatzes 21 des Hohlzylinders 4 von der Federkraft einer Rückstellfeder 10 beaufschlagt. Steigt der Druck im Speichervolumen 8 an, bewegt sich die Speicherhülse 9 entgegen der Federkraft der Rückstellfeder 10, so dass sich das Speichervolumen 8 vergrößert. Dies ist der Fall, wenn der Pumpenkolben 2 einen Arbeitshub ausführt und sich dadurch das Volumen des mit dem Speichervolumen 8 gekoppelten zweiten Druckraums 7 verkleinert. Die Volumenverkleinerung des zweiten Druckraums 7 wird dann durch eine Volumenvergrößerung des Speichervolumens 8 kompensiert. Zugleich wird die Rückstellfeder 10 weiter gespannt. Die Rückstellfeder 10 ist maximal gespannt, wenn die Speicherhülse 9 an einem Gehäuseteil 32 anschlägt, das gemeinsam mit dem Hohlzylinder 4 einen Niederdruckraum 17 begrenzt, in dem die Rückstellfeder 10 aufgenommen ist.To bring about the resetting of the pump piston 2, the second pressure chamber 7 is coupled to a storage volume 8, which is also designed as an annular space and is delimited by the hollow cylinder 4 and a storage sleeve 9 guided in a reciprocating manner on the hollow cylinder 4. For this purpose, the hollow cylinder 4 has an outer contour 20 with an annular shoulder 21 which merges into a guide surface 23 for the storage sleeve 9. The storage sleeve 9 in turn has a stepped inner contour 24 to limit the storage volume 8. In addition, the storage sleeve is acted upon in the direction of the shoulder 21 of the hollow cylinder 4 by the spring force of a return spring 10. If the pressure in the storage volume 8 increases, the storage sleeve 9 moves against the spring force of the return spring 10, so that the storage volume 8 increases. This is the case when the pump piston 2 executes a working stroke and as a result the volume of the second pressure chamber 7 coupled to the storage volume 8 is reduced. The reduction in volume of the second pressure chamber 7 is then compensated for by increasing the volume of the storage volume 8. At the same time, the return spring 10 is further tensioned. The restoring spring 10 is tensioned to the maximum when the storage sleeve 9 strikes a housing part 32 which, together with the hollow cylinder 4, delimits a low-pressure space 17 in which the restoring spring 10 is accommodated.

Hat der Pumpenkolben 2 seine obere Endlage erreicht (siehe Fig. 2), gibt er einen Verbindungskanal 11 frei, in dem ein Rückschlagventil 12 angeordnet ist, das einen Zustrom von hydraulischem Druckmittel in das Speichervolumen 8 und in den zweiten Druckraum 7 ermöglicht. Auf diese Weise wird ein Druckausgleich in den beiden Druckräumen 5, 7 erreicht, der zur Ausbildung eines hydraulischen Anschlags führt. Das heißt, dass der Arbeitshub des Pumpenkolbens 2 hydraulisch begrenzt wird, wodurch der Verschleiß am Pumpenkolben 2 reduziert wird.When the pump piston 2 has reached its upper end position (see Fig. 2 ), it releases a connecting channel 11 in which a check valve 12 is arranged, which enables an inflow of hydraulic pressure medium into the storage volume 8 and into the second pressure chamber 7. In this way, pressure equalization is achieved in the two pressure chambers 5, 7, which leads to the formation of a hydraulic stop. This means that the working stroke of the pump piston 2 is limited hydraulically, as a result of which the wear on the pump piston 2 is reduced.

Während das hydraulische Druckmittel aus dem ersten Druckraum 5 in das Speichervolumen 8 und den zweiten Druckraum 7 strömt, wird durch ein Druckbegrenzungsventil 13 verhindert, dass der hydraulische Druck über einen vorgegebenen Grenzwert steigt. Dadurch ist sichergestellt, dass die Federkraft der gespannten Rückstellfeder 10 ausreicht, den Saughub des Pumpenkolbens 2 einzuleiten. Dabei drückt die Rückstellfeder 10 die Speicherhülse 9 in Richtung des Absatzes 21 des Hohlzylinders 4, so dass sich das Speichervolumen 8 verkleinert. Zugleich sinkt die Federkraft und damit der Druck im Druckraum 7, der jedoch noch ausreichend hoch ist, so dass der Pumpenkolben 2 zurückgestellt wird. Währenddessen verhindert das im Verbindungskanal 11 angeordnete Rückschlagventil 12, dass hydraulisches Druckmittel in den ersten Druckraum 5 zurückströmt (siehe Fig. 3).While the hydraulic pressure medium flows from the first pressure chamber 5 into the storage volume 8 and the second pressure chamber 7, a pressure relief valve 13 prevents the hydraulic pressure from rising above a predetermined limit value. This ensures that the spring force of the tensioned return spring 10 is sufficient to initiate the suction stroke of the pump piston 2. The return spring 10 presses the storage sleeve 9 in the direction of the shoulder 21 of the hollow cylinder 4, so that the storage volume 8 is reduced. At the same time, the spring force drops and thus the pressure in the pressure chamber 7, which, however, is still sufficiently high so that the pump piston 2 is reset. Meanwhile, the check valve 12 arranged in the connecting channel 11 prevents hydraulic pressure medium from flowing back into the first pressure chamber 5 (see FIG Fig. 3 ).

Bei der in den Figuren 4 und 5 dargestellten Ausführungsform einer Kolbenpumpe 1 für eine erfindungsgemäße Kraftstofffördereinrichtung wird auf ein Druckbegrenzungsventil 13 verzichtet. Eine Entlastung des Speichervolumens 8 wird hier über mehrere Entlastungsöffnungen 16 erreicht, die als Radialbohrungen in der Speicherhülse 9 ausgebildet sind. Die Entlastungsöffnungen 16 werden über den Hub der Speicherhülse 9 gesteuert, wobei über die Entlastungsöffnungen 16 eine Verbindung des Speichervolumens 8 mit dem Niederdruckraum 17 herstellbar ist (siehe Fig. 5). Der sich dann einstellende Druckausgleich bewirkt eine hydraulische Begrenzung des Hubs der Speicherhülse 9, so dass ein mechanisches Anschlagen der Speicherhülse 9 am Gehäuseteil 32 verhindert wird. Dadurch kann der Verschließ an der Speicherhülse 9 bzw. am Gehäuseteil 32 verringert werden. Die in den Niederdruckraum 17 gelangende Menge des hydraulischen Druckmittels kann über eine Leckageleitung 14 und/oder eine Rücklaufleitung 19 abgeführt werden, so dass der Druck im Niederdruckraum 17 nicht über einen vorgegebenen Grenzwert ansteigt.In the case of the Figures 4 and 5 The illustrated embodiment of a piston pump 1 for a fuel delivery device according to the invention does not have a pressure limiting valve 13. Relief of the storage volume 8 is achieved here via a plurality of relief openings 16 which are designed as radial bores in the storage sleeve 9. The relief openings 16 are controlled via the stroke of the storage sleeve 9, it being possible to establish a connection between the storage volume 8 and the low-pressure chamber 17 via the relief openings 16 (see FIG Fig. 5 ). The pressure equalization that then occurs causes a hydraulic limitation of the stroke of the storage sleeve 9, so that a mechanical impact of the storage sleeve 9 on the housing part 32 is prevented. As a result, the closure on the storage sleeve 9 or on the housing part 32 can be reduced. The amount of hydraulic pressure medium reaching the low-pressure chamber 17 can be discharged via a leakage line 14 and / or a return line 19 so that the pressure in the low-pressure chamber 17 does not rise above a predetermined limit value.

Bei der in den Figuren 6 und 7 dargestellten Ausführungsform einer Kolbenpumpe 1 für eine erfindungsgemäße Kraftstofffördereinrichtung wird ebenfalls auf ein Druckbegrenzungsventil 13 verzichtet. Im Unterschied zur Ausführungsform der Figuren 4 und 5 wird eine Entlastung des Speichervolumens 8 über einen Entlastungskanal 15 bewirkt, der im Hohlzylinder 4 ausgebildet ist und - in Abhängigkeit von der Lage der Speicherhülse 9 in Bezug auf den Hohlzylinder 4 - das Speichervolumen 8 mit dem Niederdruckraum 17 verbindet. Die Funktionsweise gleicht im Übrigen der der Ausführungsform der Figuren 4 und 5, so dass hierauf verwiesen wird.In the case of the Figures 6 and 7 The illustrated embodiment of a piston pump 1 for a fuel delivery device according to the invention is also dispensed with a pressure limiting valve 13. In contrast to the embodiment of the Figures 4 and 5 Relief of the storage volume 8 is effected via a relief channel 15 which is formed in the hollow cylinder 4 and - depending on the position of the storage sleeve 9 in relation to the hollow cylinder 4 - connects the storage volume 8 to the low-pressure chamber 17. The mode of operation is otherwise the same as that of the embodiment of FIG Figures 4 and 5 so that reference is made to it.

Der Fig. 8 ist eine weitere bevorzugte Ausführungsform einer Kolbenpumpe 1 für eine erfindungsgemäße Kraftstofffördereinrichtung zu entnehmen. Die Entlastung des Speichervolumens 8 wird hier über einen Ringspalt 18 bewirkt, der sich in Abhängigkeit von der Lage der Speicherhülse 9 in Bezug auf den Hohlzylinder 4 zwischen der Speicherhülse 9 und dem Hohlzylinder 4 ausbildet. Die Speicherhülse 9 löst sich dabei über ihren gesamten Umfang von der Führungsfläche 23 des Hohlzylinders 4. Um bei der Rückstellung der Speicherhülse 9 das Wiedereintauchen des Hohlzylinders 4 in die Speicherhülse 9 zu erleichtern, weisen der Hohlzylinder 4 und die Speicherhülse 9 jeweils einen Konus 22, 25 auf. Der Konus 22 des Hohlzylinders 4 verbindet den Absatz 21 mit der Führungsfläche 23 und der Konus 25 der Speicherhülse 9 endet an einer Stirnfläche 26. Der Ringspalt 18 gewährleistet ein gleichmäßiges Abströmen des hydraulischen Druckmittels aus dem Speichervolumen 8 in den Niederdruckraum 17.Of the Fig. 8 a further preferred embodiment of a piston pump 1 for a fuel delivery device according to the invention can be found. The relief of the storage volume 8 is brought about here via an annular gap 18 which, depending on the position of the storage sleeve 9 in relation to the hollow cylinder 4, is formed between the storage sleeve 9 and the hollow cylinder 4. The storage sleeve 9 detaches itself over its entire circumference from the guide surface 23 of the hollow cylinder 4. In order to facilitate the re-immersion of the hollow cylinder 4 in the storage sleeve 9 when the storage sleeve 9 is reset, the hollow cylinder 4 and the storage sleeve 9 each have a cone 22, 25 on. The cone 22 of the hollow cylinder 4 connects the shoulder 21 with the guide surface 23 and the cone 25 of the storage sleeve 9 ends at an end face 26. The annular gap 18 ensures a uniform outflow of the hydraulic pressure medium from the storage volume 8 into the low-pressure chamber 17.

Die Ausführungsformen ohne Druckbegrenzungsventil 13 haben gemeinsam, dass die Rückstellfeder 10 die Speicherhülse 9 zurückstellt, bis die Verbindung des Speichervolumens 8 mit dem Niederdruckraum 17 über die Entlastungsöffnungen 16, den Entlastungskanal 15 oder den Ringspalt 18 wieder verschlossen ist. Die Konstruktion wird so ausgelegt, dass das zu diesem Zeitpunkt vorhandene Volumen ausreicht, die Rückstellung des Pumpenkolbens 2 zu bewirken.The embodiments without pressure relief valve 13 have in common that the return spring 10 resets the storage sleeve 9 until the connection between the storage volume 8 and the low-pressure chamber 17 via the relief openings 16, the relief channel 15 or the annular gap 18 is closed again. The construction is designed in such a way that the volume present at this point in time is sufficient to bring about the return of the pump piston 2.

Bei den Ausführungsformen mit Druckbegrenzungsventil 13 wird - wenn die Speicherhülse 9 auf Block geht bzw. ihre obere Endlage erreicht hat - über den Verbindungskanal 11 nachströmendes hydraulisches Druckmittel über das Druckbegrenzungsventil 13 abgeführt. Auch hier wird die Konstruktion so ausgelegt, dass das zu diesem Zeitpunkt vorhandene Volumen ausreicht, die Rückstellung des Pumpenkolbens 2 zu bewirken.In the embodiments with a pressure limiting valve 13, hydraulic pressure medium flowing in via the connecting channel 11 is discharged via the pressure limiting valve 13 when the storage sleeve 9 becomes blocked or has reached its upper end position. Here, too, the construction is designed in such a way that the volume present at this point in time is sufficient to bring about the return of the pump piston 2.

Claims (9)

  1. Fuel delivery device for cryogenic fuels, comprising a piston pump (1) for delivering the cryogenic fuel at high pressure, wherein the piston pump (1) has a pump piston (2) which is movable back and forth, said pump piston, at one end, delimiting a compression chamber (3) and, at the other end, delimiting a pressure chamber (5) which is formed in a hollow cylinder (4) and can be charged with a hydraulic pressure medium,
    characterized in that the pump piston (2) has an annular shoulder (6) for delimiting a further pressure chamber (7), which is formed in the hollow cylinder (4) and, for the return movement of the pump piston (2), can likewise be charged with the hydraulic pressure medium, wherein the further pressure chamber (7) is coupled to an accumulator volume (8) which is delimited by an accumulator sleeve (9), said accumulator sleeve being arranged on the hollow cylinder (4) so as to be movable back and forth and being preloaded by means of a return spring (10).
  2. Fuel delivery device according to Claim 1,
    characterized in that the accumulator volume (8), in dependence on the position of the pump piston (2), preferably in an upper end position of the pump piston (2), can be connected hydraulically to the first pressure chamber (5) via a connecting channel (11) formed in the hollow cylinder (4).
  3. Fuel delivery device according to Claim 2,
    characterized in that a check valve (12) is arranged in the connecting channel (11) and prevents the hydraulic pressure medium from flowing from the accumulator volume (8) back into the first pressure chamber (5).
  4. Fuel delivery device according to one of the preceding claims,
    characterized in that the accumulator volume (8) can be connected to a leakage line (14) via a pressure-limiting valve (13).
  5. Fuel delivery device according to one of the preceding claims,
    characterized in that the accumulator volume (8), in dependence on the position of the accumulator sleeve (9), can be connected to a low-pressure chamber (17) via at least one relief channel (15) formed in the hollow cylinder (4) or via at least one relief opening (16) formed in the accumulator sleeve (9).
  6. Fuel delivery device according to one of Claims 1 to 4,
    characterized in that the accumulator volume (8), in dependence on the position of the accumulator sleeve (9), can be connected to a low-pressure chamber (17) via an annular gap (18) between the hollow cylinder (4) and the accumulator sleeve (9).
  7. Fuel delivery device according to Claim 5 or 6,
    characterized in that the low-pressure chamber (17) is connected to a tank for the hydraulic pressure medium via a return line (19) and/or via the leakage line (14), wherein preferably the hydraulic pressure medium is an oil, in particular an engine oil.
  8. Fuel delivery device according to one of the preceding claims,
    characterized in that, for forming the accumulator volume (8), the hollow cylinder (4) has a stepped outer contour (20) with an annular shoulder (21), which preferably transitions into a guide surface (23) for the accumulator sleeve (9) via a cone (22).
  9. Fuel delivery device according to one of the preceding claims,
    characterized in that, for delimiting the accumulator volume (8), the accumulator sleeve (9) has a stepped inner contour (24), which preferably transitions at one end into a face surface (26) via a cone (25).
EP18800579.7A 2017-12-11 2018-11-07 Fuel delivery device for cryogenic fuels Active EP3724501B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017012218.0A DE102017012218A1 (en) 2017-12-11 2017-12-11 Fuel delivery device for cryogenic fuels
PCT/EP2018/080447 WO2019115097A1 (en) 2017-12-11 2018-11-07 Fuel delivery device for cryogenic fuels

Publications (2)

Publication Number Publication Date
EP3724501A1 EP3724501A1 (en) 2020-10-21
EP3724501B1 true EP3724501B1 (en) 2021-11-03

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ID=64270857

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Application Number Title Priority Date Filing Date
EP18800579.7A Active EP3724501B1 (en) 2017-12-11 2018-11-07 Fuel delivery device for cryogenic fuels

Country Status (4)

Country Link
EP (1) EP3724501B1 (en)
CN (1) CN111527308B (en)
DE (1) DE102017012218A1 (en)
WO (1) WO2019115097A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110131129A (en) * 2019-05-05 2019-08-16 英嘉动力科技无锡有限公司 A kind of new structure cryogenic pump
CN114962844B (en) * 2022-04-26 2023-07-21 重庆海浦洛自动化科技有限公司 Energy storage device for high-viscosity medium and use method thereof

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6354088B1 (en) * 2000-10-13 2002-03-12 Chart Inc. System and method for dispensing cryogenic liquids
CA2362844C (en) * 2001-11-30 2004-08-31 Westport Research Inc. Method and apparatus for delivering a high pressure gas from a cryogenic storage tank
CN101691854A (en) * 2009-10-14 2010-04-07 同济大学 Novel fuel pressurization pump and pressurization system
EP2541062A1 (en) 2011-06-29 2013-01-02 Westport Power Inc. Cryogenic pump
US9228574B2 (en) * 2013-02-27 2016-01-05 Caterpillar Inc. Hydraulic relief and switching logic for cryogenic pump system
CN104279135B (en) * 2013-07-11 2018-10-16 西港能源有限公司 Low-pressure low-temperature pump group part
US10024311B2 (en) * 2015-08-06 2018-07-17 Caterpillar Inc. Cryogenic pump for liquefied natural gas
DK179219B1 (en) * 2016-05-26 2018-02-12 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland Fuel or lubrication pump for a large two-stroke compression-ignited internal combustion engine

Also Published As

Publication number Publication date
DE102017012218A1 (en) 2019-06-13
EP3724501A1 (en) 2020-10-21
WO2019115097A1 (en) 2019-06-20
CN111527308B (en) 2022-07-19
CN111527308A (en) 2020-08-11

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