EP3189227B1 - High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine - Google Patents

High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine Download PDF

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Publication number
EP3189227B1
EP3189227B1 EP15738071.8A EP15738071A EP3189227B1 EP 3189227 B1 EP3189227 B1 EP 3189227B1 EP 15738071 A EP15738071 A EP 15738071A EP 3189227 B1 EP3189227 B1 EP 3189227B1
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EP
European Patent Office
Prior art keywords
pump
chamber
cylinder bore
fuel
feed line
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15738071.8A
Other languages
German (de)
French (fr)
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EP3189227A1 (en
Inventor
Achim Koehler
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP3189227A1 publication Critical patent/EP3189227A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means preventing fuel leakage around pump plunger, e.g. fluid barriers
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0054—Check 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0452—Distribution members, e.g. 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/90—Selection of particular materials
    • F02M2200/9015—Elastomeric or plastic materials

Definitions

  • the invention relates to a high-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure fuel pump and a fuel injection device is characterized by the DE 10 2012 218 552 A1 known.
  • This high-pressure fuel pump has at least one pump element, which in turn has a pump piston driven in a stroke movement.
  • the pump piston is slidably guided in a cylinder bore of a housing part of the pump and delimited in the cylinder bore a pump working space, wherein an inlet valve is provided, through which the pump working space is connectable to a fuel inlet.
  • the pump piston projects with its end facing away from the pump working space out of the pump working RAM remote from the end of the cylinder bore.
  • a sealing ring is provided on the protruding from the cylinder bore end portion of the pump piston.
  • the sealing ring serves to avoid mixing of the fuel pumped by the pump piston with the medium present outside the cylinder bore of the housing part.
  • the medium present outside the cylinder bore of the housing part is in particular lubricating oil for lubricating a drive region, for example a roller tappet and its support on a cam.
  • the sealing ring has on its inner circumference at least one sealing lip, with which it bears against the pump piston.
  • the sealing ring is in a surrounding of the cylinder bore end region of the pump piston receptacle of the Pump housing part arranged. Between the sealing ring and the pump housing part, a space is limited to the cylinder bore, which is separated from the sealing ring by a portion of the pump housing part.
  • the space is connected to a fuel delivery port to the intake valve with the fuel delivery passage passing through the space.
  • An inlet section of the fuel delivery inlet leading from a feed pump opens into a first peripheral area of the room and a second inlet section of the fuel feed inlet discharging from the room leads away from a second peripheral area of the room deviating from the first peripheral area.
  • the high-pressure fuel pump according to the invention with the features of claim 1 has the advantage that the thermal load of the sealing ring is further reduced, since the space is constantly flowed through by the bypass connection of fuel, which flows into the discharge area, regardless of the fuel delivery of the pump element.
  • FIG. 1 a pump in a longitudinal section
  • FIG. 2 one in FIG. 1 With II designated section of the pump in an enlarged view.
  • FIG. 1 is shown in a simplified representation of a pump, which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine.
  • the high-pressure fuel pump has at least one pump element 10, which in turn has a pump piston 12 which is driven at least indirectly by a drive shaft 14 in a lifting movement in at least approximately radial direction with respect to the axis of rotation 15 of the drive shaft 14.
  • the drive shaft 14 may be part of the pump or alternatively may also be provided that the pump does not have its own drive shaft and the drive shaft 14 is part of the internal combustion engine.
  • the drive shaft 14 may be, for example, a shaft of the internal combustion engine through which the gas exchange valves of the internal combustion engine are actuated.
  • the drive shaft 14 has a cam 16 or eccentric for driving the pump piston 12.
  • the pump has a pump housing, which may be designed in several parts.
  • the pump piston 12 is tightly guided in a cylinder bore 18 of a housing part 20 of the pump wherein the housing part 20 is referred to below as the cylinder head.
  • the pump piston 12 in the cylinder bore 18 defines a pump working chamber 22.
  • the pump working chamber 22 has a connection via an inlet valve 24, which may be an inlet check valve opening into the pump working chamber 22 or an electrically, in particular electromagnetically controlled valve with a fuel delivery inlet 26, via which the pump working chamber 22 is filled with the radially inward to the rotational axis 15 of the drive shaft 14 directed suction stroke of the pump piston 12 with fuel.
  • the fuel delivery inlet 26 is fed, for example, by a feed pump 27, is conveyed by the fuel from a fuel tank 25.
  • the pump chamber 22 also has an outlet valve 28, which is, for example, an outlet check valve opening out of the pump working space 22 Connection to a drain 30, which can lead to a high-pressure accumulator 32 and over the radially outward from the rotational axis 15 of the drive shaft 14 directed away pumping stroke 12 of the pump piston 12 fuel is displaced from the pump working chamber 22.
  • the pump piston 12 is supported via a roller tappet 40 on the cam 16 of the drive shaft 14.
  • the roller tappet 40 has a tappet body 42 in which a roller 44 rolling on the cam 16 is rotatably mounted.
  • the plunger body 42 is acted upon by a spring 46 toward the cam 16, so that the roller 44 remains in contact with the cam 16 during the suction stroke of the pump piston 12.
  • the pump piston 12 projects with its end facing away from the pump working chamber 22 out of the cylinder bore 18 and is coupled at its end to the plunger body 42, so that the pump piston 12 is also acted upon by the spring 46.
  • the pump piston 12 may have at its projecting from the cylinder bore 18 end in diameter relative to the guided in the cylinder bore 18 shaft enlarged piston 48.
  • the cylinder head 20 has in the region of the cylinder bore 18 to the cam 16 toward a cylinder bore 18 surrounding at least approximately cylindrical portion 50.
  • the spring 46 is formed as a cylindrical helical compression spring, surrounds the portion 50 of the cylinder head 20 and is supported on the cylinder head 20 from.
  • a sealing ring 52 is provided which surrounds the end region of the pump piston 12 projecting from the cylinder bore 18 on its circumference.
  • the sealing ring 52 is under radial bias with at least one arranged on the inner circumference elastic sealing lip 54 on the pump piston 12 at.
  • the at least one sealing lip 54 preferably has a surface with a low coefficient of friction, at least in the region of its contact with the pump piston 12, in order to cause only slight frictional forces during the lifting movement of the pump piston 12.
  • the sealing ring 52 has two or three sealing lips 54 spaced from one another in the direction of the longitudinal axis 13 of the pump piston 12.
  • the sealing ring 52 is made of PTFE, polytetrafluoroethylene, for example.
  • the portion 50 of the cylinder head 20 has at its end to the cylinder bore 18 at least approximately coaxial bore 58 which has a larger diameter than the cylinder bore 18 and which forms a receptacle for the sealing ring 52.
  • an annular shoulder 60 is formed at the transition from the bore 58 to the cylinder bore 18.
  • the sealing ring 52 is secured in the receptacle 58 in the direction of the longitudinal axis 13 of the pump piston 12 by a holding element 64.
  • the holding member 64 may be, for example, a resilient ring which is engaged in an annular groove 68 in the inner periphery of the receptacle 58.
  • the holding element 64 may also be formed, for example, as a disk, which is for example pressed into the receptacle 58 or fastened in some other way.
  • the sealing ring 52 is sleeve-shaped and on the inside of which at least one sealing lip 54 is formed.
  • the sealing ring 52 may each have an annular groove 70 at its two axial end faces pointing in the direction of the longitudinal axis 13 of the pump piston 12. By the annular grooves 70 it is achieved that the axial edge regions of the sealing ring 52 are radially elastically deformable.
  • a spring 72 may be inserted in the annular grooves 70, by which a radial bias of the sealing ring 52 is generated with its at least one sealing lip 54 on the pump piston 12.
  • a space 74 is limited, in which passes in the stroke movement of the pump piston 12 between this and the cylinder bore 18 from the pump working chamber 22 leaking leakage fuel.
  • the space 74 may be extended by an annular groove 76 surrounding the end region of the cylinder bore 18.
  • the fuel delivery inlet 26 has a first inlet section 26 a, which leads from the feed pump 27 into the space 74 and a second inlet section 26 b, which leads from the space 74 to the inlet valve 24.
  • the confluence of the second inlet section 26b in the space 74 is located in a different peripheral region of the space 74 than the confluence of the first inlet section 26a, wherein the junctions of the inlet sections 26a, 26b are in particular diametrically opposite each other with respect to the longitudinal axis 13 of the pump piston 12.
  • the inlet sections 26a, 26b are designed, for example, in the form of bores in the cylinder head 20.
  • a bypass connection 78 branches off from the second inlet section 26b upstream of the inlet valve 24 and leads into a relief region, for example into a return line to the fuel tank 25.
  • the bypass connection 78 it is possible that a flow through the space 74 takes place even if there is no supply of fuel via the inlet valve 24 into the pump working chamber 22, the inlet valve 24 is thus closed. In this case, fuel can flow into the discharge area via the bypass connection 78.
  • a pressure valve 80 is arranged in the bypass connection 78, which releases the bypass connection 78 only when the opening pressure of the pressure valve 80 in the inlet section 26b is exceeded.
  • a throttle 82 may also be arranged in the bypass connection 78 in order to limit the flow through the bypass connection 78.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Details Of Reciprocating Pumps (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffhochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a high-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.

Eine solche Kraftstoffhochdruckpumpe und eine Kraftstoffeinspritzeinrichtung ist durch die DE 10 2012 218 552 A1 bekannt. Diese Kraftstoffhochdruckpumpe weist wenigstens ein Pumpenelement auf, das wiederum einen einen in einer Hubbewegung angetriebenen Pumpenkolben aufweist. Der Pumpenkolben ist in einer Zylinderbohrung eines Gehäuseteils der Pumpe verschiebbar geführt und begrenzt in der Zylinderbohrung einen Pumpenarbeitsraum, wobei ein Einlassventil vorgesehen ist, durch das der Pumpenarbeitsraum mit einem Kraftstoffzulauf verbindbar ist. Der Pumpenkolben ragt mit seinem dem Pumpenarbeitsraum abgewandten Ende aus dem dem Pumpenarbeitsram abgewandten Ende der Zylinderbohrung heraus. Auf dem aus der Zylinderbohrung ragenden Endbereich des Pumpenkolbens ist ein Dichtring vorgesehen. Der Dichtring dient dazu eine Vermischung von dem durch den Pumpenkolben geförderten Kraftstoff mit dem außerhalb der Zylinderbohrung des Gehäuseteils vorhandenen Medium zu vermeiden. Das außerhalb der Zylinderbohrung des Gehäuseteils vorhandene Medium ist insbesondere Schmieröl zur Schmierung eines Antriebsbereichs, beispielsweise einem Rollenstößel und dessen Abstützung an einem Nocken. Der Dichtring weist an seinem Innenumfang wenigstens eine Dichtlippe auf, mit der er am Pumpenkolben anliegt. Der Dichtring ist in einer den aus der Zylinderbohrung ragenden Endbereich des Pumpenkolbens umgebenden Aufnahme des Pumpengehäuseteils angeordnet. Zwischen dem Dichtring und dem Pumpengehäuseteil ist zur Zylinderbohrung hin ein Raum begrenzt, der vom Dichtring durch einen Abschnitt des Pumpengehäuseteils getrennt ist. Der Raum ist mit einem Kraftstoffförderzulauf zum Einlassventil verbunden, wobei der Kraftstoffförderzulauf durch den Raum verläuft. Ein von einer Förderpumpe herführender Zulaufabschnitt des Kraftstoffförderzulaufs mündet in einem ersten Umfangsbereich des Raums ein und ein zweiter vom Raum abführender Zulaufabschnitt des Kraftstoffförderzulaufs führt von einem vom ersten Umfangsbereich abweichenden zweiten Umfangsbereich des Raums ab. Bei geöffnetem Einlassventil wird dabei eine Durchströmung und damit Kühlung des Raums erreicht. Wenn das Einlassventil geschlossen ist erfolgt jedoch keine Durchströmung des Raums und damit keine Kühlung. Der zweite Zulaufabschnitt des Kraftstoffförderzulaufs ist mit einem Dämpferelement verbunden, in das Kraftstoff verdrängt werden kann, jedoch erfolgt keine Durchströmung des Dämperelements.Such a high-pressure fuel pump and a fuel injection device is characterized by the DE 10 2012 218 552 A1 known. This high-pressure fuel pump has at least one pump element, which in turn has a pump piston driven in a stroke movement. The pump piston is slidably guided in a cylinder bore of a housing part of the pump and delimited in the cylinder bore a pump working space, wherein an inlet valve is provided, through which the pump working space is connectable to a fuel inlet. The pump piston projects with its end facing away from the pump working space out of the pump working RAM remote from the end of the cylinder bore. On the protruding from the cylinder bore end portion of the pump piston, a sealing ring is provided. The sealing ring serves to avoid mixing of the fuel pumped by the pump piston with the medium present outside the cylinder bore of the housing part. The medium present outside the cylinder bore of the housing part is in particular lubricating oil for lubricating a drive region, for example a roller tappet and its support on a cam. The sealing ring has on its inner circumference at least one sealing lip, with which it bears against the pump piston. The sealing ring is in a surrounding of the cylinder bore end region of the pump piston receptacle of the Pump housing part arranged. Between the sealing ring and the pump housing part, a space is limited to the cylinder bore, which is separated from the sealing ring by a portion of the pump housing part. The space is connected to a fuel delivery port to the intake valve with the fuel delivery passage passing through the space. An inlet section of the fuel delivery inlet leading from a feed pump opens into a first peripheral area of the room and a second inlet section of the fuel feed inlet discharging from the room leads away from a second peripheral area of the room deviating from the first peripheral area. When the inlet valve is open, a flow and thus cooling of the room is achieved. When the inlet valve is closed, however, there is no flow through the room and thus no cooling. The second inlet section of the fuel delivery inlet is connected to a damper element, can be displaced into the fuel, however, there is no flow through the Dämperelements.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffhochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass die thermische Belastung des Dichtrings weiter verringert ist, da der Raum durch die Bypassverbindung ständig von Kraftstoff durchströmt ist, der in den Entlastungsbereich abströmt, unabhängig von der Kraftstoffförderung des Pumpenelements.The high-pressure fuel pump according to the invention with the features of claim 1 has the advantage that the thermal load of the sealing ring is further reduced, since the space is constantly flowed through by the bypass connection of fuel, which flows into the discharge area, regardless of the fuel delivery of the pump element.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffhochdruckpumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine wirkungsvolle Durchströmung des gesamten Raums sichergestellt.In the dependent claims advantageous refinements and developments of the high-pressure fuel pump according to the invention are given. The embodiment according to claim 2 ensures an effective flow through the entire space.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Pumpe in einem Längsschnitt und Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Pumpe in vergrößerter Darstellung.An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Show it FIG. 1 a pump in a longitudinal section and FIG. 2 one in FIG. 1 With II designated section of the pump in an enlarged view.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist in vereinfachter Darstellung eine Pumpe gezeigt, die insbesondere eine Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist. Die Kraftstoffhochdruckpumpe weist wenigstens ein Pumpenelement 10 auf, das wiederum einen Pumpenkolben 12 aufweist, der zumindest mittelbar durch eine Antriebswelle 14 in einer Hubbewegung in zumindest annähernd radialer Richtung bezüglich der Drehachse 15 der Antriebswelle 14 angetrieben wird. Die Antriebswelle 14 kann Teil der Pumpe sein oder alternativ kann auch vorgesehen sein, dass die Pumpe keine eigene Antriebswelle aufweist und die Antriebswelle 14 Teil der Brennkraftmaschine ist. Die Antriebswelle 14 kann dabei beispielsweise eine Welle der Brennkraftmaschine sein durch die auch die Gaswechselventile der Brennkraftmaschine betätigt werden. Die Antriebswelle 14 weist für den Antrieb des Pumpenkolbens 12 einen Nocken 16 oder Exzenter auf.In FIG. 1 is shown in a simplified representation of a pump, which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine. The high-pressure fuel pump has at least one pump element 10, which in turn has a pump piston 12 which is driven at least indirectly by a drive shaft 14 in a lifting movement in at least approximately radial direction with respect to the axis of rotation 15 of the drive shaft 14. The drive shaft 14 may be part of the pump or alternatively may also be provided that the pump does not have its own drive shaft and the drive shaft 14 is part of the internal combustion engine. The drive shaft 14 may be, for example, a shaft of the internal combustion engine through which the gas exchange valves of the internal combustion engine are actuated. The drive shaft 14 has a cam 16 or eccentric for driving the pump piston 12.

Die Pumpe weist ein Pumpengehäuse auf, das mehrteilig ausgebildet sein kann. Der Pumpenkolben 12 ist in einer Zylinderbohrung 18 eines Gehäuseteils 20 der Pumpe dicht geführt wobei das Gehäuseteil 20 nachfolgend als Zylinderkopf bezeichnet wird. Mit seinem der Antriebswelle 14 abgewandten Ende begrenzt der Pumpenkolben 12 in der Zylinderbohrung 18 einen Pumpenarbeitsraum 22. Der Pumpenarbeitsraum 22 weist über ein Einlassventil 24, das ein in den Pumpenarbeitsraum 22 hinein öffnendes Einlassrückschlagventil oder ein elektrisch, insbesondere elektromagnetisch gesteuertes Ventil sein kann, eine Verbindung mit einem Kraftstoffförderzulauf 26 auf, über den der Pumpenarbeitsraum 22 beim radial nach innen zur Drehachse 15 der Antriebswelle 14 gerichteten Saughub des Pumpenkolbens 12 mit Kraftstoff befüllt wird. Der Kraftstoffförderzulauf 26 wird beispielsweise von einer Förderpumpe 27 gespeist, durch die Kraftstoff aus einem Kraftstoffvorratsbehälter 25 gefördert wird. Der Pumpenarbeitsraum 22 weist außerdem über ein Auslassventil 28, das beispielsweise ein aus dem Pumpenarbeitsraum 22 heraus öffnendes Auslassrückschlagventil ist, eine Verbindung mit einem Ablauf 30 auf, der zu einem Hochdruckspeicher 32 führen kann und über den beim radial nach außen von der Drehachse 15 der Antriebswelle 14 weg gerichteten Förderhub des Pumpenkolbens 12 Kraftstoff aus dem Pumpenarbeitsraum 22 verdrängt wird.The pump has a pump housing, which may be designed in several parts. The pump piston 12 is tightly guided in a cylinder bore 18 of a housing part 20 of the pump wherein the housing part 20 is referred to below as the cylinder head. With its end facing away from the drive shaft 14, the pump piston 12 in the cylinder bore 18 defines a pump working chamber 22. The pump working chamber 22 has a connection via an inlet valve 24, which may be an inlet check valve opening into the pump working chamber 22 or an electrically, in particular electromagnetically controlled valve with a fuel delivery inlet 26, via which the pump working chamber 22 is filled with the radially inward to the rotational axis 15 of the drive shaft 14 directed suction stroke of the pump piston 12 with fuel. The fuel delivery inlet 26 is fed, for example, by a feed pump 27, is conveyed by the fuel from a fuel tank 25. The pump chamber 22 also has an outlet valve 28, which is, for example, an outlet check valve opening out of the pump working space 22 Connection to a drain 30, which can lead to a high-pressure accumulator 32 and over the radially outward from the rotational axis 15 of the drive shaft 14 directed away pumping stroke 12 of the pump piston 12 fuel is displaced from the pump working chamber 22.

Der Pumpenkolben 12 stützt sich über einen Rollenstößel 40 am Nocken 16 der Antriebswelle 14 ab. Der Rollenstößel 40 weist einen Stößelkörper 42 auf, in dem eine auf dem Nocken 16 abrollende Rolle 44 drehbar gelagert ist. Der Stößelkörper 42 wird durch eine Feder 46 zum Nocken 16 hin beaufschlagt, so dass die Rolle 44 auch beim Saughub des Pumpenkolbens 12 in Anlage am Nocken 16 bleibt. Der Pumpenkolben 12 ragt mit seinem dem Pumpenarbeitsraum 22 abgewandten Ende aus der Zylinderbohrung 18 heraus und ist an seinem Ende mit dem Stößelkörper 42 gekoppelt, so dass der Pumpenkolben 12 ebenfalls durch die Feder 46 beaufschlagt ist. Der Pumpenkolben 12 kann an seinem aus der Zylinderbohrung 18 ragenden Ende einen im Durchmesser gegenüber dem in der Zylinderbohrung 18 geführten Schaft vergrößerten Kolbenfuß 48 aufweisen. Der Zylinderkopf 20 weist im Bereich der Zylinderbohrung 18 zum Nocken 16 hin einen die Zylinderbohrung 18 umgebenden zumindest annähernd zylinderförmigen Abschnitt 50 auf. Die Feder 46 ist als zylindrische Schraubendruckfeder ausgebildet, umgibt den Abschnitt 50 des Zylinderkopfs 20 und stützt sich am Zylinderkopf 20 ab.The pump piston 12 is supported via a roller tappet 40 on the cam 16 of the drive shaft 14. The roller tappet 40 has a tappet body 42 in which a roller 44 rolling on the cam 16 is rotatably mounted. The plunger body 42 is acted upon by a spring 46 toward the cam 16, so that the roller 44 remains in contact with the cam 16 during the suction stroke of the pump piston 12. The pump piston 12 projects with its end facing away from the pump working chamber 22 out of the cylinder bore 18 and is coupled at its end to the plunger body 42, so that the pump piston 12 is also acted upon by the spring 46. The pump piston 12 may have at its projecting from the cylinder bore 18 end in diameter relative to the guided in the cylinder bore 18 shaft enlarged piston 48. The cylinder head 20 has in the region of the cylinder bore 18 to the cam 16 toward a cylinder bore 18 surrounding at least approximately cylindrical portion 50. The spring 46 is formed as a cylindrical helical compression spring, surrounds the portion 50 of the cylinder head 20 and is supported on the cylinder head 20 from.

Es ist ein Dichtring 52 vorgesehen, der den aus der Zylinderbohrung 18 ragenden Endbereich des Pumpenkolbens 12 auf dessen Umfang umgibt. Der Dichtring 52 liegt unter radialer Vorspannung mit wenigstens einer an dessen Innenumfang angeordneten elastischen Dichtlippe 54 am Pumpenkolben 12 an. Die wenigstens eine Dichtlippe 54 weist vorzugsweise zumindest im Bereich ihrer Anlage am Pumpenkolben 12 eine Oberfläche mit geringem Reibungskoeffizienten auf, um bei der Hubbewegung des Pumpenkolbens 12 nur geringe Reibungskräfte zu verursachen. Vorzugsweise weist der Dichtring 52 zwei oder drei in Richtung der Längsachse 13 des Pumpenkolbens 12 zueinander beabstandete Dichtlippen 54 auf. Der Dichtring 52 ist beispielsweise aus PTFE, Polytetrafluorethylen, hergestellt.A sealing ring 52 is provided which surrounds the end region of the pump piston 12 projecting from the cylinder bore 18 on its circumference. The sealing ring 52 is under radial bias with at least one arranged on the inner circumference elastic sealing lip 54 on the pump piston 12 at. The at least one sealing lip 54 preferably has a surface with a low coefficient of friction, at least in the region of its contact with the pump piston 12, in order to cause only slight frictional forces during the lifting movement of the pump piston 12. Preferably, the sealing ring 52 has two or three sealing lips 54 spaced from one another in the direction of the longitudinal axis 13 of the pump piston 12. The sealing ring 52 is made of PTFE, polytetrafluoroethylene, for example.

Der Abschnitt 50 des Zylinderkopfs 20 weist an seinem Ende eine zur Zylinderbohrung 18 zumindest annähernd koaxiale Bohrung 58 auf, die einen größeren Durchmesser als die Zylinderbohrung 18 aufweist und die eine Aufnahme für den Dichtring 52 bildet. Am Übergang von der Bohrung 58 zur Zylinderbohrung 18 ist eine Ringschulter 60 gebildet. Der Dichtring 52 wird in der Aufnahme 58 in Richtung der Längsachse 13 des Pumpenkolbens 12 durch ein Halteelement 64 gesichert. Das Halteelement 64 kann beispielsweise ein federnder Ring sein, der in eine Ringnut 68 im Innenumfang der Aufnahme 58 eingerastet ist. Alternativ kann das Halteelement 64 auch beispielsweise als Scheibe ausgebildet sein, die beispielsweise in die Aufnahme 58 eingepresst ist oder auf andere Weise befestigt ist.The portion 50 of the cylinder head 20 has at its end to the cylinder bore 18 at least approximately coaxial bore 58 which has a larger diameter than the cylinder bore 18 and which forms a receptacle for the sealing ring 52. At the transition from the bore 58 to the cylinder bore 18, an annular shoulder 60 is formed. The sealing ring 52 is secured in the receptacle 58 in the direction of the longitudinal axis 13 of the pump piston 12 by a holding element 64. The holding member 64 may be, for example, a resilient ring which is engaged in an annular groove 68 in the inner periphery of the receptacle 58. Alternatively, the holding element 64 may also be formed, for example, as a disk, which is for example pressed into the receptacle 58 or fastened in some other way.

Der Dichtring 52 ist hülsenförmig ausgebildet und an dessen Innenseite ist die wenigstens eine Dichtlippe 54 ausgebildet. Der Dichtring 52 kann an seinen beiden in Richtung der Längsachse 13 des Pumpenkolbens 12 weisenden axialen Stirnseiten jeweils eine Ringnut 70 aufweisen. Durch die Ringnuten 70 wird erreicht, dass die axialen Randbereiche des Dichtrings 52 radial elastisch verformbar sind. In den Ringnuten 70 kann jeweils eine Feder 72 eingesetzt sein, durch die eine radiale Vorspannung des Dichtrings 52 mit seiner wenigstens einen Dichtlippe 54 am Pumpenkolben 12 erzeugt wird.The sealing ring 52 is sleeve-shaped and on the inside of which at least one sealing lip 54 is formed. The sealing ring 52 may each have an annular groove 70 at its two axial end faces pointing in the direction of the longitudinal axis 13 of the pump piston 12. By the annular grooves 70 it is achieved that the axial edge regions of the sealing ring 52 are radially elastically deformable. In each case a spring 72 may be inserted in the annular grooves 70, by which a radial bias of the sealing ring 52 is generated with its at least one sealing lip 54 on the pump piston 12.

Zwischen der der Ringschulter 60 zugewandten axialen Stirnseite des Dichtrings 52 und dem Zylinderkopf 20 ist ein Raum 74 begrenzt, in den bei der Hubbewegung des Pumpenkolbens 12 zwischen diesem und der Zylinderbohrung 18 aus dem Pumpenarbeitsraum 22 austretender Leckagekraftstoff gelangt. Der Raum 74 kann durch eine den Endbereich der Zylinderbohrung 18 umgebende Ringnut 76 erweitert sein.Between the annular shoulder 60 facing axial end face of the sealing ring 52 and the cylinder head 20, a space 74 is limited, in which passes in the stroke movement of the pump piston 12 between this and the cylinder bore 18 from the pump working chamber 22 leaking leakage fuel. The space 74 may be extended by an annular groove 76 surrounding the end region of the cylinder bore 18.

Es ist vorgesehen, dass der zum Einlassventil 24 führende Kraftstoffförderzulauf 26 durch den Raum 74 geführt ist. Der Kraftstoffförderzulauf 26 weist einen ersten Zulaufabschnitt 26a auf, der von der Förderpumpe 27 in den Raum 74 führt und einen zweiten Zulaufabschnitt 26b, der vom Raum 74 zum Einlassventil 24 führt. Die Einmündung des zweiten Zulaufabschnitts 26b in den Raum 74 liegt in einem anderen Umfangsbereich des Raums 74 als die Einmündung des ersten Zulaufabschnitts 26a, wobei die Einmündungen der Zulaufabschnitte 26a,26b insbesondere einander bezüglich der Längsachse 13 des Pumpenkolbens 12 diametral gegenüberliegen. Hierdurch ist sichergestellt, dass der Raum 74 möglichst vollständig von dem durch den Kraftstoffzulauf 26 strömenden Kraftstoff durchströmt wird und somit erhitzter Leckagekraftstoff mitgeführt wird, so dass die Temperaturbelastung des Dichtrings 52 gering ist. Die Zulaufabschnitte 26a,26b sind beispielsweise in Form von Bohrungen im Zylinderkopf 20 ausgeführt.It is envisaged that the leading to the inlet valve 24 fuel delivery inlet 26 is guided through the space 74. The fuel delivery inlet 26 has a first inlet section 26 a, which leads from the feed pump 27 into the space 74 and a second inlet section 26 b, which leads from the space 74 to the inlet valve 24. The confluence of the second inlet section 26b in the space 74 is located in a different peripheral region of the space 74 than the confluence of the first inlet section 26a, wherein the junctions of the inlet sections 26a, 26b are in particular diametrically opposite each other with respect to the longitudinal axis 13 of the pump piston 12. This ensures that the space 74 flows through the fuel flowing through the fuel inlet 26 as completely as possible and thus heated leakage fuel is carried, so that the temperature load of the sealing ring 52 is low. The inlet sections 26a, 26b are designed, for example, in the form of bores in the cylinder head 20.

Erfindungsgemäß ist vorgesehen, dass von dem zweiten Zulaufabschnitt 26b stromaufwärts vor dem Einlassventil 24 eine Bypassverbindung 78 abzweigt, die in einen Entlastungsbereich, beispielsweise in einen Rücklauf zum Kraftstoffvorratsbehälter 25 führt. Durch die Bypassverbindung 78 ist es ermöglicht, dass eine Durchströmung des Raums 74 auch dann erfolgt, wenn keine Zuführung von Kraftstoff über das Einlassventil 24 in den Pumpenarbeitsraum 22 erfolgt, das Einlassventil 24 also geschlossen ist. In diesem Fall kann über die Bypassverbindung 78 Kraftstoff in den Entlastungsbereich abströmen. Es kann vorgesehen sein, dass in der Bypassverbindung 78 ein Druckventil 80 angeordnet ist, das die Bypassverbindung 78 nur bei Überschreiten des Öffnungsdrucks des Druckventils 80 im Zulaufabschnitt 26b freigibt. Alternativ oder zusätzlich kann in der Bypassverbindung 78 auch eine Drossel 82 angeordnet sein, um den Durchfluss durch die Bypassverbindung 78 zu begrenzen.According to the invention, a bypass connection 78 branches off from the second inlet section 26b upstream of the inlet valve 24 and leads into a relief region, for example into a return line to the fuel tank 25. By the bypass connection 78, it is possible that a flow through the space 74 takes place even if there is no supply of fuel via the inlet valve 24 into the pump working chamber 22, the inlet valve 24 is thus closed. In this case, fuel can flow into the discharge area via the bypass connection 78. It can be provided that a pressure valve 80 is arranged in the bypass connection 78, which releases the bypass connection 78 only when the opening pressure of the pressure valve 80 in the inlet section 26b is exceeded. Alternatively or additionally, a throttle 82 may also be arranged in the bypass connection 78 in order to limit the flow through the bypass connection 78.

Durch die Anlage des Außenmantels des Dichtrings 52 am radialen Innenmantel der Aufnahme 58 ergibt sich eine Vorspannung in radialer Richtung auf den Dichtring 52. Außerdem erfolgt zwischen dem Außenmantel des Dichtrings 52 und dem Innenmantel der Aufnahme 58 eine statische Abdichtung, durch die verhindert wird, dass Schmieröl zur Zylinderbohrung 18 gelangt und durch den Pumpenkolben 12 bei dessen Hubbewegung in die Zylinderbohrung 18 verschleppt wird und sich mit dem Kraftstoff vermischt.By applying the outer shell of the sealing ring 52 on the radial inner surface of the receptacle 58 results in a bias in the radial direction on the sealing ring 52. In addition, between the outer shell of the sealing ring 52 and the inner surface of the receptacle 58 is a static seal, is prevented by Lubricating oil to the cylinder bore 18 passes and is dragged by the pump piston 12 in the stroke movement in the cylinder bore 18 and mixed with the fuel.

Beim Betrieb der Pumpe wird durch den Pumpenkolben 12 Kraftstoff gefördert, der im Pumpenarbeitsraum 22 vorhanden ist und der infolge des erforderlichen Spiels zwischen dem Pumpenkolben 12 und der Zylinderbohrung 18 und des im Pumpenarbeitsraum 22 herrschenden hohen Drucks auch aus der Zylinderbohrung 18 in den Raum 74 und in die Ringnut 76 austreten kann. Durch die Kraftstoffströmung im Kraftstoffzulauf 26 wird der erhitzte Leckagekraftstoff aus dem Raum 74 und der Ringnut 76 abgeleitet und dem Einlassventil 24 zugeführt. Durch den Dichtring 52 wird sowohl die Leckage von Kraftstoff aus der Zylinderbohrung 18 und dem Raum 74 in den Schmierölkreislauf als auch die Leckage von Schmieröl aus dem Schmierölkreislauf in den Raum 74 und weiter in die Zylinderbohrung 18 verhindert oder zumindest gering gehalten.During operation of the pump 12 fuel is pumped through the pump piston, which is present in the pump working chamber 22 and due to the required clearance between the pump piston 12 and the cylinder bore 18 and the pressure prevailing in the pump working chamber 22 high pressure from the Cylinder bore 18 can escape into the space 74 and into the annular groove 76. Due to the fuel flow in the fuel inlet 26, the heated leakage fuel from the space 74 and the annular groove 76 is derived and fed to the inlet valve 24. By the sealing ring 52, both the leakage of fuel from the cylinder bore 18 and the space 74 in the lubricating oil circuit and the leakage of lubricating oil from the lubricating oil circuit in the space 74 and further into the cylinder bore 18 is prevented or at least kept low.

Claims (4)

  1. Pump, in particular high-pressure fuel pump for a fuel injection device of an internal combustion engine, having at least one pump element (10) which has a pump piston (12) driven in a reciprocating movement, which pump piston is guided displaceably in a cylinder bore (18) of a housing part (20) of the pump and delimits a pump working chamber (22) in said cylinder bore, wherein an inlet valve (24) is provided by means of which the pump working chamber (22) is connectable to a fuel delivery feed line (26), wherein the pump piston (12) projects with its end averted from the pump working chamber (22) out of the cylinder bore (18), wherein, on that end region of the pump piston (12) which projects out of the cylinder bore (18), there is arranged a sealing ring (52) which, at its inner circumference, bears with a sealing lip (54) against the pump piston (12), wherein the sealing ring (52) is arranged in a receptacle (58, 60) of the pump housing part (20), which receptacle surrounds that end region of the pump piston (12) which projects out of the cylinder bore (18), wherein, between the sealing ring (52) and the pump housing part (20), toward the cylinder bore (18), a chamber (74; 76) is delimited which is connected by means of the fuel delivery feed line (26) to the inlet valve (24), wherein the fuel delivery feed line (26) runs through the chamber (74; 76), and wherein a first feed line portion (26a), which leads in from a delivery pump (27), of the fuel delivery feed line (26) opens into a first circumferential region of the chamber (74), and a second feed line portion (26b), which leads away from the chamber (74), of the fuel delivery feed line (26) leads away from a second circumferential region, which differs from the first circumferential region, of the chamber (74), characterized in that the chamber (74) is delimited by the sealing ring (52), and in that, from the second feed line portion (26b) which leads away from the chamber (74), a bypass connection (78) leads away into a relief region (25), via which bypass connection fuel can flow out into the relief region (25) when the inlet valve (24) is closed.
  2. Pump according to Claim 1, characterized in that the second circumferential region of the chamber (74) is situated at least approximately diametrically opposite the first circumferential region.
  3. Pump according to Claim 1 or 2, characterized in that the chamber (74) is formed at least partially by a ring-shaped groove (76), which surrounds the pump piston (12) and adjoins the sealing ring (52), in the pump housing part (20).
  4. Pump according to any of Claims 1 to 3, characterized in that a pressure valve (80) and/or a throttle (82) is arranged in the bypass connection (78).
EP15738071.8A 2014-09-01 2015-07-14 High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine Active EP3189227B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014217388.4A DE102014217388A1 (en) 2014-09-01 2014-09-01 High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine
PCT/EP2015/066025 WO2016034316A1 (en) 2014-09-01 2015-07-14 High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP3189227A1 EP3189227A1 (en) 2017-07-12
EP3189227B1 true EP3189227B1 (en) 2019-02-27

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EP15738071.8A Active EP3189227B1 (en) 2014-09-01 2015-07-14 High-pressure fuel pump, in particular for a fuel injection device of an internal combustion engine

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EP (1) EP3189227B1 (en)
JP (1) JP2017529485A (en)
KR (1) KR20170044754A (en)
CN (1) CN106662062B (en)
DE (1) DE102014217388A1 (en)
WO (1) WO2016034316A1 (en)

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DE102016114148A1 (en) * 2016-08-01 2018-02-01 L'orange Gmbh High pressure pump, in particular for fuel injection
IT201700065545A1 (en) * 2017-06-13 2018-12-13 Bosch Gmbh Robert PUMP UNIT FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE
IT201700098475A1 (en) * 2017-09-01 2019-03-01 Bosch Gmbh Robert PUMP UNIT FOR FUEL SUPPLY TO AN INTERNAL COMBUSTION ENGINE
DE102020114417A1 (en) * 2020-05-29 2021-12-02 Liebherr-Components Deggendorf Gmbh high pressure pump

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JP4215000B2 (en) * 2005-01-19 2009-01-28 株式会社デンソー High pressure pump
JP5002351B2 (en) * 2007-06-28 2012-08-15 本田技研工業株式会社 Scooter type vehicle
US7677872B2 (en) * 2007-09-07 2010-03-16 Gm Global Technology Operations, Inc. Low back-flow pulsation fuel injection pump
DE102008040452A1 (en) * 2008-07-16 2010-01-21 Robert Bosch Gmbh High pressure pump for fuel injection device, particularly common rail injection system for injecting fuel into combustion chamber of internal combustion engine, has compressor chamber that is connected to storage space
DE102008042649B4 (en) * 2008-10-07 2017-07-27 Robert Bosch Gmbh Plug-in pump with integrated low-pressure pump
US7827967B2 (en) * 2008-10-23 2010-11-09 Gm Global Technology Operations, Inc. Low noise fuel pump with variable pressure regulation
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JP5321432B2 (en) * 2009-12-03 2013-10-23 株式会社デンソー Fuel supply device
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CN106662062B (en) 2019-07-26
DE102014217388A1 (en) 2016-03-03
CN106662062A (en) 2017-05-10
EP3189227A1 (en) 2017-07-12
JP2017529485A (en) 2017-10-05
WO2016034316A1 (en) 2016-03-10
KR20170044754A (en) 2017-04-25

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