DE102005046670A1 - High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet - Google Patents

High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet Download PDF

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Publication number
DE102005046670A1
DE102005046670A1 DE102005046670A DE102005046670A DE102005046670A1 DE 102005046670 A1 DE102005046670 A1 DE 102005046670A1 DE 102005046670 A DE102005046670 A DE 102005046670A DE 102005046670 A DE102005046670 A DE 102005046670A DE 102005046670 A1 DE102005046670 A1 DE 102005046670A1
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Germany
Prior art keywords
plunger
pump
ball
longitudinal axis
pressure pump
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DE102005046670A
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German (de)
Inventor
Alfons Schoetz
Gerhard Meier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to DE102005046670A priority Critical patent/DE102005046670A1/en
Priority to EP06793348A priority patent/EP1931875B1/en
Priority to PCT/EP2006/066162 priority patent/WO2007036423A1/en
Priority to AT06793348T priority patent/ATE460584T1/en
Priority to DE502006006407T priority patent/DE502006006407D1/en
Publication of DE102005046670A1 publication Critical patent/DE102005046670A1/en
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M59/102—Mechanical drive, e.g. tappets or cams

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

Abstract

The pump has a pump piston (20) that is indirectly supported in a drive shaft by a hollow cylindrical tappet (40). The tappet is displaceably guided in a bore (42) of a part of a base plate (14) in a direction of the longitudinal axis (21) of the piston. The tappet has a groove (56) running in the direction of a longitudinal axis (41) of the tappet. A ball (58) is indirectly fixed in a part of the plate in a tangential direction to the tappet and is engaged in the groove approximately radial to the longitudinal axis (41). A rolling friction exists between the ball and the tappet.

Description

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

Eine solche Hochdruckpumpe ist durch die DE 199 07 311 A1 bekannt. Diese Hochdruckpumpe weist ein Pumpengehäuse und wenigstens ein im Pumpengehäuse angeordnetes Pumpenelement auf. Das Pumpenelement weist einen durch eine Antriebswelle der Hochdruckpumpe in einer Hubbewegung angetriebenen Pumpenkolben auf. Der Pumpenkolben ist in einer Zylinderbohrung eines Pumpengehäuseteils der Hochdruckpumpe dicht geführt und begrenzt in der Zylinderbohrung einen Pumpenarbeitsraum. Der Pumpenkolben stützt sich zumindest mittelbar über einen hohlzylinderförmigen Stößel an der Antriebswelle ab. Der Stößel ist in einer Bohrung eines Pumpengehäuseteils in Richtung der Längsachse des Pumpenkolbens verschiebbar geführt. Unter Umständen kann es zu einer Verdrehung des Stößels um seine Längsachse in der Bohrung kommen, wodurch ein erhöhter Verschleiss des Stößels und/oder des Pumpengehäuses sowie gegebenenfalls weiterer Teile der Hochdruckpumpe verursacht wird. Übliche Verdrehsicherungen für den Stößel sind aufwendig in der Herstellung und Montage.Such a high-pressure pump is through the DE 199 07 311 A1 known. This high-pressure pump has a pump housing and at least one pump element arranged in the pump element. The pump element has a driven by a drive shaft of the high pressure pump in a stroke pump piston. The pump piston is tightly guided in a cylinder bore of a pump housing part of the high-pressure pump and delimits a pump working space in the cylinder bore. The pump piston is supported at least indirectly via a hollow-cylindrical ram on the drive shaft. The plunger is slidably guided in a bore of a pump housing part in the direction of the longitudinal axis of the pump piston. Under certain circumstances, there may be a rotation of the plunger about its longitudinal axis in the bore, whereby increased wear of the plunger and / or the pump housing and possibly other parts of the high-pressure pump is caused. Conventional anti-rotation for the ram are expensive to manufacture and assembly.

Vorteile der ErfindungAdvantages of invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass eine Verdrehsicherung des Stößels mit einfachen Mitteln gewährleistet ist. Bei der Kugel handelt es sich um ein Standardteil, das als Zulieferteil kostengünstig erworben werden kann.The High pressure pump according to the invention with the features according to claim 1 has in contrast the advantage that an anti-rotation of the plunger with simple means guaranteed is. The ball is a standard part, as a vendor part economical can be purchased.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Hochdruckpumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine geringe Reibung bei der Verdrehsicherung des Stößels erreicht, da zumindest an einer Abstützung der Kugel am Stößel Rollreibung vorliegt. Durch die Ausbildung gemäß Anspruch 3 wird eine sichere Anlage der Kugel in der Nut des Stößels erreicht. Durch die Ausbildung gemäß Anspruch 4 wird eine besonders geringe Reibung erreicht, da sowohl zwischen der Kugel und dem Stößel als auch zwischen der Kugel und der Aufnahme Rollreibung vorliegt. Durch die Ausbildung gemäß Anspruch 8 ist eine besonders einfache Montage der Aufnahme und der Kugel ermöglicht.In the dependent claims are advantageous embodiments and refinements of the high-pressure pump according to the invention specified. The training according to claim 2 is a small Friction achieved in the rotation of the plunger, since at least on a support the ball on the ram rolling friction is present. The training according to claim 3 is a safe Investment of the ball reached in the groove of the plunger. Through the training according to claim 4 a particularly low friction is achieved because both between the ball and the pestle as also exists between the ball and the recording rolling friction. By the training according to claim 8 is a particularly simple mounting of the receptacle and the ball allows.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine in einem Längsschnitt, 2 einen in 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe in vergrößerter Darstellung gemäß einem ersten Ausführungsbeispiel, 3 die Hochdruckpumpe in einem Schnitt entlang Linie III-III in 2, 4 einen in 3 mit IV bezeichneten Ausschnitt in nochmals vergrößerter Darstellung und 5 den Ausschnitt II der Hochdruckpumpe gemäß einem zweiten Ausführungsbeispiel.Two embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. Show it 1 a high-pressure pump for a fuel injection device of an internal combustion engine in a longitudinal section, 2 one in 1 with II designated section of the high pressure pump in an enlarged view according to a first embodiment, 3 the high-pressure pump in a section along line III-III in 2 . 4 one in 3 with IV designated section in a further enlarged view and 5 the detail II of the high pressure pump according to a second embodiment.

Beschreibung der Ausführungsbeispieledescription the embodiments

In den 1 bis 5 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein mehrteiliges Pumpengehäuse 10 auf, in dem eine durch die Brennkraftmaschine rotierend angetriebene Antriebswelle 12 angeordnet ist. Die Antriebswelle 12 ist beispielsweise über zwei in Richtung der Drehachse 13 der Antriebswelle 12 voneinander beabstandete Lagerstellen drehbar gelagert. Die Lagerstellen können in verschiedenen Teilen des Pumpengehäuses 10 angeordnet sein, beispielsweise kann eine erste Lagerstelle in einem Grundkörper 14 des Pumpengehäuses 10 und eine zweite Lagerstelle in einem mit dem Grundkörper 14 verbundenen Flanschteil 15 angeordnet sein.In the 1 to 5 a high pressure pump for a fuel injector of an internal combustion engine is shown. The high-pressure pump has a multipart pump housing 10 in, in which a drive shaft rotatably driven by the internal combustion engine 12 is arranged. The drive shaft 12 is for example about two in the direction of the axis of rotation 13 the drive shaft 12 rotatably mounted bearing points spaced apart. The bearings can be in different parts of the pump housing 10 can be arranged, for example, a first bearing in a body 14 of the pump housing 10 and a second bearing in one with the body 14 connected flange part 15 be arranged.

In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 12 wenigstens einen Nocken 16 oder einen exzentrisch zu ihrer Drehachse 13 ausgebildeten Abschnitt auf, wobei der Nocken 16 auch als Mehrfachnocken ausgebildet sein kann. Die Hochdruckpumpe weist wenigstens ein oder mehrere im Gehäuse 10 angeordnete Pumpenelemente 18 mit jeweils einem Pumpenkolben 20 auf, der durch den Nocken 16 der Antriebswelle 12 in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 13 der Antriebswelle 12 angetrieben wird. Im Bereich jedes Pumpenelements 18 ist ein mit dem Grundkörper 14 verbundenes Pumpengehäuseteil 22 vorgesehen, das als Zylinderkopf ausgebildet ist. Das Pumpengehäuseteil 22 weist einen an einer Außenseite des Grundkörpers 14 anliegenden Flansch 24 und einen durch eine Öffnung im Grundkörper 14 zur Antriebswelle 12 hin durchragenden, zumindest annähernd zylinderförmigen Ansatz 26 mit gegenüber dem Flansch 24 kleinerem Durchmesser auf. Der Pumpenkolben 20 ist in einer im Ansatz 26 ausgebildeten Zylinderbohrung 28 im Pumpengehäuseteil 22 dicht verschiebbar geführt und begrenzt mit seiner der Antriebswelle 12 abgewandten Stirnseite in der Zylinderbohrung 28 einen Pumpenarbeitsraum 30. Die Zylinderbohrung 28 kann sich bis in den Flansch 24 hinein erstrecken, in dem dann der Pumpenarbeitsraum 30 angeordnet ist. Der Pumpenarbeitsraum 30 weist über einen im Pumpengehäuse 10 verlaufenden Kraftstoffzulaufkanal 32 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Förderpumpe auf. An der Mündung des Kraftstoffzulaufkanals 32 in den Pumpenarbeitsraum 30 ist ein in den Pumpenarbeitsraum 30 öffnendes Einlassventil 34 angeordnet. Der Pumpenarbeitsraum 30 weist ausserdem über einen im Pumpengehäuse 10 verlaufenden Kraftstoffablaufkanal 36 eine Verbindung mit einem Auslass auf, der beispielsweise mit einem Hochdruckspeicher 110 verbunden ist. Mit dem Hochdruckspeicher 110 sind ein oder vorzugsweise mehrere an den Zylindern der Brennkraftmaschine angeordnete Injektoren 120 verbunden, durch die Kraftstoff in die Zylinder der Brennkraftmaschine eingespritzt wird. An der Mündung des Kraftstoffablaufkanals 36 in den Pumpenarbeitsraum 30 ist ein aus dem Pumpenarbeitsraum 30 öffnendes Auslassventil 38 angeordnet.In a lying between the two bearing areas area, the drive shaft 12 at least one cam 16 or an eccentric to its axis of rotation 13 trained section on, with the cam 16 can also be designed as a multiple cam. The high pressure pump has at least one or more in the housing 10 arranged pump elements 18 each with a pump piston 20 on that by the cam 16 the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 the drive shaft 12 is driven. In the area of each pump element 18 is one with the main body 14 connected pump housing part 22 provided, which is designed as a cylinder head. The pump housing part 22 has one on an outer side of the body 14 adjacent flange 24 and one through an opening in the body 14 to the drive shaft 12 protruding, at least approximately cylindrical approach 26 with respect to the flange 24 smaller diameter. The pump piston 20 is in an approach 26 trained cylinder bore 28 in the pump housing part 22 tightly displaceable leads and limits with its the drive shaft 12 opposite end face in the cylinder bore 28 a pump workroom 30 , The cylinder bore 28 can get up in the flange 24 into which then the pump workspace 30 is arranged. The pump workroom 30 has one in the pump housing 10 extending fuel inlet channel 32 a connection with a fuel inlet, for example, a feed pump. At the mouth of the fuel inlet duct 32 into the pump workroom 30 is one in the pump work space 30 opening inlet valve 34 arranged. The pump workroom 30 also has a in the pump housing 10 extending fuel drain channel 36 a connection with an outlet, for example, with a high-pressure accumulator 110 connected is. With the high-pressure accumulator 110 are one or preferably a plurality of arranged on the cylinders of the internal combustion engine injectors 120 is connected, is injected through the fuel into the cylinders of the internal combustion engine. At the mouth of the fuel drainage channel 36 into the pump workroom 30 is one out of the pump workroom 30 opening exhaust valve 38 arranged.

Zwischen dem Pumpenkolben 20 und dem Nocken 16 der Antriebswelle 12 ist ein Stößel 40 angeordnet, über den sich der Pumpenkolben 20 zumindest mittelbar am Nocken 16 der Antriebswelle 12 abstützt. Der Stößel 40 ist hohlzylinderförmig mit rundem Außenquerschnitt ausgebildet und ist in einer Bohrung 42 des Grundkörpers 14 des Pumpengehäuses 10 in Richtung der Längsachse 21 des Pumpenkolbens 20 verschiebbar geführt. Die Längsachse 41 des Stößels 40 ist somit zumindest im wesentlichen identisch mit der Längsachse 21 des Pumpenkolbens 20. Im Stößel 40 ist in dessen der Antriebswelle 12 zugewandtem Endbereich ein Stützelement 44 eingesetzt, in dem eine Rolle 46 drehbar gelagert ist, die auf dem Nocken 16 der Antriebswelle 12 abrollt. Die Drehachse 47 der Rolle 46 ist zumindest annähernd parallel zur Drehachse 13 der Antriebswelle 12. Das Stützelement 44 weist auf seiner der Antriebswelle 12 zugewandten Seite eine Vertiefung 48 auf, in der die Rolle 46 gelagert ist.Between the pump piston 20 and the cam 16 the drive shaft 12 is a pestle 40 arranged over which the pump piston 20 at least indirectly on the cam 16 the drive shaft 12 supported. The pestle 40 is formed in a hollow cylindrical shape with a round outer cross section and is in a bore 42 of the basic body 14 of the pump housing 10 in the direction of the longitudinal axis 21 of the pump piston 20 slidably guided. The longitudinal axis 41 of the plunger 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20 , In the pestle 40 is in the drive shaft 12 facing end a support element 44 used in which a role 46 is rotatably mounted on the cam 16 the drive shaft 12 rolls. The rotation axis 47 the role 46 is at least approximately parallel to the axis of rotation 13 the drive shaft 12 , The support element 44 indicates on its the drive shaft 12 facing side of a depression 48 on, in which the role 46 is stored.

Am Stößel 40 oder am Pumpenkolben 20 greift eine vorgespannte Rückstellfeder 52 an, die sich am Pumpengehäuseteil 22 abstützt. Durch die Rückstellfeder 52 werden der Pumpenkolben 20 und der Stößel 40 zum Nocken 16 der Antriebswelle 12 hin beaufschlagt, so dass die Anlage der Rolle 44 am Nocken 16 auch beim zur Antriebswelle 12 hin gerichteten Saughub des Pumpenkolbens 20 und auch bei hoher Drehzahl der Antriebswelle 12 sichergestellt ist. Der Pumpenkolben 20 kann mit dem Stößel 40 gekoppelt sein, zumindest in Richtung von dessen Längsachse 21. Alternativ kann der Pumpenkolben 20 auch nicht mit dem Stößel 40 verbunden sein, wobei dann durch die Rückstellfeder 52 die Anlage des Pumpenkolbens 20 am Stößel 40 sichergestellt wird. Es kann vorgesehen sein, dass die Rückstellfeder 52 beispielsweise über einen Federteller 53 an einem im Durchmesser vergrößerten Kolbenfuß des Pumpenkolbens 20 angreift, der dadurch in Anlage an einem am Stößel 40 von dessen Mantel nach innen ragenden Flansch gehalten wird, der wiederum in Anlage am Stützelement 44 gehalten wird, so dass der gesamte Verbund aus Pumpenkolben 20, Stößel 40 und Stützelement 44 mit Rolle 46 zum Nocken 16 der Antriebswelle 12 hin beaufschlagt ist.At the pestle 40 or on the pump piston 20 engages a preloaded return spring 52 attached to the pump housing part 22 supported. By the return spring 52 become the pump piston 20 and the pestle 40 to the cam 16 the drive shaft 12 acted upon so that the attachment of the role 44 on the cam 16 also to the drive shaft 12 directed suction stroke of the pump piston 20 and also at high speed of the drive shaft 12 is ensured. The pump piston 20 can with the pestle 40 be coupled, at least in the direction of its longitudinal axis 21 , Alternatively, the pump piston 20 not even with the pestle 40 be connected, in which case by the return spring 52 the system of the pump piston 20 on the pestle 40 is ensured. It can be provided that the return spring 52 for example, via a spring plate 53 on a diameter enlarged piston foot of the pump piston 20 engages thereby in abutment with a ram 40 is held by the jacket inwardly projecting flange, in turn, in contact with the support element 44 is held, so that the entire composite of pump piston 20 , Pestle 40 and support element 44 with role 46 to the cam 16 the drive shaft 12 is acted upon.

Im Außenmantel des Stößels 40 ist wenigstens eine in Richtung von dessen Längsachse 41 verlaufende Nut 56 angeordnet, die vorzugsweise im Querschnitt zumindest annähernd kreisabschnittförmig geformt ist. In die Nut 56 greift zumindest annähernd radial zur Längsachse 41 des Stößels 40 eine Kugel 58 mit einem Teil ihres Umfangs ein, die im Pumpengehäuse 10 in tangentialer Richtung zum Stößel 40 fixiert ist. In den 2 bis 4 ist die Hochdruckpumpe gemäß einem ersten Ausführungsbeispiel dargestellt, bei dem die Kugel 58 in einer Aufnahme 60 in Richtung der Längsachse 41 des Stößels 40 beweglich geführt ist. Die Aufnahme 60 weist dabei wie in 2 und 4 dargestellt eine rinnenförmige Vertiefung 62 auf, die im Querschnitt senkrecht zur Längsachse 41 des Stößels 40 zumindest im wesentlichen prismatisch ausgebildet ist und zwei einander gegenüberliegende schräge Wände aufweist, an denen die Kugel 58 jeweils anliegt. Die Kugel 58 taucht mit einem Teil ihres Umfangs in die Vertiefung 62 ein und ist dadurch in tangentialer Richtung des Stößels 40 fixiert, so dass der Stößel 40 durch die Kugel 58 gegen Verdrehen um seine Längsachse 41 gesichert ist. Bei der Hubbewegung des Stößels 40 zusammen mit dem Pumpenkolben 20 rollt die Kugel 58 sowohl in der Nut 56 des Stößels 40 als auch in der Vertiefung 62 der Aufnahme 60 ab, so dass nur eine geringe Rollreibung auftritt.In the outer jacket of the ram 40 is at least one in the direction of its longitudinal axis 41 running groove 56 arranged, which is preferably at least approximately circular section shaped in cross section. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the plunger 40 a ball 58 with a part of its circumference, in the pump housing 10 in a tangential direction to the ram 40 is fixed. In the 2 to 4 the high pressure pump according to a first embodiment is shown, in which the ball 58 in a recording 60 in the direction of the longitudinal axis 41 of the plunger 40 is movably guided. The recording 60 points as in 2 and 4 illustrated a trough-shaped depression 62 on, in cross-section perpendicular to the longitudinal axis 41 of the plunger 40 is formed at least substantially prismatic and has two opposing inclined walls, where the ball 58 in each case. The ball 58 dives with part of its circumference into the depression 62 and is thereby in the tangential direction of the plunger 40 fixed, leaving the ram 40 through the ball 58 against twisting about its longitudinal axis 41 is secured. During the stroke movement of the plunger 40 together with the pump piston 20 rolls the ball 58 both in the groove 56 of the plunger 40 as well as in the depression 62 the recording 60 from, so that only a small rolling friction occurs.

Die Aufnahme 60 ist wie in den 2 und 3 dargestellt beispielsweise in einer zumindest annähernd radial bezüglich der Längsachse 41 des Stößels 40 angeordneten Bohrung 64 im Grundkörper 14 des Pumpengehäuses 10 eingesetzt. Die Aufnahme 60 ist dabei zylinderförmig ausgebildet, wobei auf deren dem Stößel 40 zugewandten Innenseite die Vertiefung 62 ausgebildet ist. Die Bohrung 64 ist zur Außenseite des Grundkörpers 14 des Pumpengehäuses 10 hin mittels eines Stopfens 66 verschlossen. Zwischen dem Stopfen 66 und der Aufnahme 60 ist vorzugsweise eine vorgespannte Feder 68, beispielsweise eine Schraubendruckfeder, eingespannt, durch die die in der Bohrung 64 verschiebbare Aufnahme 60 und damit die Kugel 58 zum Stößel 40 hin gepresst wird. In einer Ringnut des Stopfens 66 kann ein elastischer Dichtring 70, beispielsweise ein O-Ring, angeordnet sein, um das Innere des Pumpengehäuses 10 nach außen abzudichten. Es kann vorgesehen sein, dass der Stopfen 66 in die Bohrung 64 eingeschraubt oder eingepresst ist. Außerdem kann vorgesehen sein, dass das Flanschteil 15 in mit dem Grundkörper 14 zusammengebautem Zustand die Bohrung 64 zumindest teilweise überdeckt und somit den Stopfen 66 in der Bohrung 64 sichert. Die Aufnahme 60 mit der Kugel 58, der Stopfen 66 und die Feder 68 werden vor dem Zusammenbau des Pumpengehäuses 10 in die Bohrung 64 von der Außenseite des Grundkörpers 14 her eingesetzt. Bei der Montage der Aufnahme 60 muss sichergestellt sein, dass deren Vertiefung 62 exakt parallel zur Nut 56 des Stößels 40 ausgerichtet ist, um die Hubbewegung des Stößels 40 bei geringstmöglicher Reibung zu ermöglichen.The recording 60 is like in the 2 and 3 represented for example in an at least approximately radially with respect to the longitudinal axis 41 of the plunger 40 arranged bore 64 in the main body 14 of the pump housing 10 used. The recording 60 is cylindrical, wherein on the ram 40 facing inside the recess 62 is trained. The hole 64 is to the outside of the body 14 of the pump housing 10 out by means of a plug 66 locked. Between the stopper 66 and the recording 60 is preferably a preloaded spring 68 , For example, a helical compression spring, clamped by the in the bore 64 movable recording 60 and with it the ball 58 to the pestle 40 is pressed out. In an annular groove of the plug 66 can be an elastic sealing ring 70 For example, an O-ring may be disposed around the interior of the pump housing 10 seal to the outside. It can be provided that the plug 66 into the hole 64 screwed or pressed. In addition, it can be provided that the flange part 15 in with the main body 14 assembled state the hole 64 at least partially covered and thus the plug 66 in the hole 64 guaranteed. The recording 60 with the ball 58 , the stopper 66 and the spring 68 be before assembling the pump housing 10 into the hole 64 from the outside of the body 14 used here. When mounting the recording 60 must be ensured that their deepening 62 exactly parallel to the groove 56 of the plunger 40 is aligned to the lifting movement of the plunger 40 to allow for the least possible friction.

Die Tiefe der Nut 56 im Stößel 40 und damit die Eintauchtiefe der Kugel 58 in die Nut 56 sowie die Vorspannung der Feder 68 bestimmen die Größe des Drehmoments gegen das der Stößel 40 gegen Verdrehung gesichert werden kann. Je größer die Tiefe der Nut 56 und damit die Eintauchtiefe der Kugel 58 in diese ist und je größer die Vorspannung der Feder 68 ist, desto größer ist das Drehmoment, gegen das der Stößel 40 gegen Verdrehung gesichert werden kann.The depth of the groove 56 in the pestle 40 and thus the immersion depth of the sphere 58 in the groove 56 as well as the bias of the spring 68 determine the magnitude of the torque against that of the plunger 40 can be secured against rotation. The greater the depth of the groove 56 and thus the immersion depth of the sphere 58 in this is and the greater the bias of the spring 68 is, the greater the torque against which the plunger 40 can be secured against rotation.

In 5 ist die Hochdruckpumpe gemäß einem zweiten Ausführungsbeispiel dargestellt, bei dem der grundsätzliche Aufbau der Hochdruckpumpe gleich wie beim ersten Ausführungsbeispiel ist, jedoch die Aufnahme 160 für die Kugel 58 modifiziert ist. Die Aufnahme 160 weist auf ihrer dem Stößel 40 zugewandten Seite eine kugelkalottenförmige Vertiefung 162 auf, in der die Kugel 58 drehbar gelagert ist. Die Aufnahme 160 ist in eine Sackbohrung eines die Bohrung 64 im Grundkörper 14 des Pumpengehäuses 10 verschließenden Stopfens 166 verschiebbar eingesetzt. Zwischen dem Stopfen 166 und der Aufnahme 160 ist die vorgespannte Feder 68 angeordnet. Vorteilhaft bei der Ausführung der Hochdruckpumpe gemäß dem zweiten Ausführungsbeispiel ist, dass die Aufnahme 160 einfacher ausgebildet ist als beim ersten Ausführungsbeispiel und dass die Aufnahme 160 in beliebigen Drehstellungen in das Pumpengehäuse 10 eingesetzt werden kann. Allerdings ist beim zweiten Ausführungsbeispiel nur zwischen der Kugel 58 und dem Stößel 40 Rollreibung vorhanden, während zwischen der Kugel 58 und der Aufnahme 160 Gleitreibung vorliegt.In 5 is the high-pressure pump according to a second embodiment shown, in which the basic structure of the high-pressure pump is the same as in the first embodiment, but the recording 160 for the ball 58 is modified. The recording 160 points to her the pestle 40 facing side a spherical cap depression 162 on, in which the ball 58 is rotatably mounted. The recording 160 is in a blind hole of a bore 64 in the main body 14 of the pump housing 10 closing plug 166 slidably inserted. Between the stopper 166 and the recording 160 is the preloaded spring 68 arranged. An advantage of the embodiment of the high pressure pump according to the second embodiment is that the recording 160 is formed simpler than the first embodiment and that the recording 160 in any rotational positions in the pump housing 10 can be used. However, in the second embodiment, only between the ball 58 and the pestle 40 Rolling friction exists while in between the ball 58 and the recording 160 Sliding friction is present.

Beim Saughub des Pumpenkolbens 20, bei dem sich dieser radial nach innen bewegt, wird der Pumpenarbeitsraum 30 durch den Kraftstoffzulaufkanal 32 bei geöffnetem Einlassventil 34 mit Kraftstoff befüllt, wobei das Auslassventil 38 geschlossen ist. Beim Förderhub des Pumpenkolbens 20, bei dem sich dieser radial nach aussen bewegt, wird durch den Pumpenkolben 20 Kraftstoff unter Hochdruck durch den Kraftstoffablaufkanal 36 bei geöffnetem Auslassventil 38 zum Hochdruckspeicher 110 gefördert, wobei das Einlassventil 34 geschlossen ist.During the suction stroke of the pump piston 20 , in which this moves radially inward, the pump working space 30 through the fuel inlet channel 32 with the inlet valve open 34 filled with fuel, with the exhaust valve 38 closed is. During the delivery stroke of the pump piston 20 , in which this moves radially outward, is through the pump piston 20 Fuel under high pressure through the fuel drain channel 36 with the exhaust valve open 38 to the high-pressure accumulator 110 promoted, the inlet valve 34 closed is.

Claims (10)

Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit einem Pumpengehäuse (10, 14, 22), mit wenigstens einem Pumpenelement (18), das einen durch eine Antriebswelle (12) in einer Hubbewegung angetriebenen Pumpenkolben (20) aufweist, der in einer Zylinderbohrung (28) eines Teils des Pumpengehäuses (22) verschiebbar geführt ist und in dieser einen Pumpenarbeitsraum (30) begrenzt, wobei sich der Pumpenkolben (20) zumindest mittelbar über einen hohlzylinderförmigen Stößel (40) an der Antriebswelle (12) abstützt, wobei der Stößel (40) in einer Bohrung (42) eines Teils des Pumpengehäuses (14) in Richtung der Längsachse (21) des Pumpenkolbens (20) verschiebbar geführt ist, dadurch gekennzeichnet, dass der Stößel (40) in seinem Außenmantel eine in Richtung seiner Längsachse (41) verlaufende Nut (56) aufweist, in die zumindest annähernd radial zur Längsachse (41) des Stößels (40) eine zumindest mittelbar in einem Teil des Pumpengehäuses (14) in tangentialer Richtung zum Stößel (40) fixierte Kugel (58) zur Verdrehsicherung des Stößels (40) eingreift.High-pressure pump, in particular for a fuel injection device of an internal combustion engine, with a pump housing ( 10 . 14 . 22 ), with at least one pump element ( 18 ), one by a drive shaft ( 12 ) in a stroke-driven pump piston ( 20 ), which in a cylinder bore ( 28 ) of a part of the pump housing ( 22 ) is slidably guided and in this one pump work space ( 30 ), wherein the pump piston ( 20 ) at least indirectly via a hollow cylindrical plunger ( 40 ) on the drive shaft ( 12 ), wherein the plunger ( 40 ) in a bore ( 42 ) of a part of the pump housing ( 14 ) in the direction of the longitudinal axis ( 21 ) of the pump piston ( 20 ) is guided displaceably, characterized in that the plunger ( 40 ) in its outer jacket one in the direction of its longitudinal axis ( 41 ) running groove ( 56 ), in which at least approximately radially to the longitudinal axis ( 41 ) of the plunger ( 40 ) one at least indirectly in a part of the pump housing ( 14 ) in a tangential direction to the ram ( 40 ) fixed ball ( 58 ) for preventing rotation of the plunger ( 40 ) intervenes. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass zumindest zwischen der Kugel (58) und dem Stößel (40) Rollreibung vorliegt.High-pressure pump according to claim 1, characterized in that at least between the ball ( 58 ) and the plunger ( 40 ) Rolling friction is present. Hochdruckpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kugel (58) zumindest mittelbar durch eine vorgespannte Feder (68) in die Nut (56) des Stößels (40) gepresst wird.High-pressure pump according to claim 1 or 2, characterized in that the ball ( 58 ) at least indirectly by a prestressed spring ( 68 ) into the groove ( 56 ) of the plunger ( 40 ) is pressed. Hochdruckpumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Kugel (58) in einer im Pumpengehäuseteil (14) angeordneten Aufnahme (60) in Richtung der Längsachse (41) des Stößels (40) beweglich geführt ist.High-pressure pump according to claim 2 or 3, characterized in that the ball ( 58 ) in a pump housing part ( 14 ) arranged receptacle ( 60 ) in the direction of the longitudinal axis ( 41 ) of the plunger ( 40 ) is movably guided. Hochdruckpumpe nach Anspruch 4, dadurch gekennzeichnet, dass die Führung (62) für die Kugel (58) in der Aufnahme (60) im Querschnitt senkrecht zur Längsachse (41) des Stößels (40) zumindest annähernd prismatisch ausgebildet ist.High-pressure pump according to claim 4, characterized in that the guide ( 62 ) for the ball ( 58 ) in the recording ( 60 ) in cross-section perpendicular to the longitudinal axis ( 41 ) of the plunger ( 40 ) is formed at least approximately prismatic. Hochdruckpumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Kugel (58) in einer im Pumpengehäuseteil (14) angeordneten Aufnahme (160) drehbar gelagert ist.High-pressure pump according to claim 2 or 3, characterized in that the ball ( 58 ) in a pump housing part ( 14 ) arranged receptacle ( 160 ) is rotatably mounted. Hochdruckpumpe nach Anspruch 6, dadurch gekennzeichnet, dass die Aufnahme (160) eine zumindest annähernd kugelkalottenförmige Vertiefung (162) aufweist, in der die Kugel (58) gelagert ist.High-pressure pump according to claim 6, characterized in that the receptacle ( 160 ) an at least approximately spherical cap depression ( 162 ), in which the ball ( 58 ) is stored. Hochdruckpumpe nach einem der Ansprüche 4 bis 7, dadurch gekennzeichnet, dass die Aufnahme (60; 160) in einer Bohrung (64) im Pumpengehäuseteil (14) eingesetzt ist, vorzugsweise von einer der Bohrung (42), in der der Stößel (40) geführt ist, abgewandten Außenseite des Pumpengehäuseteils (14) her.High-pressure pump according to one of claims 4 to 7, characterized in that the receptacle ( 60 ; 160 ) in a bore ( 64 ) in the pump housing part ( 14 ) is inserted, preferably from one of the bore ( 42 ), in which the plunger ( 40 ) is guided, the opposite outer side of the pump housing part ( 14 ) ago. Hochdruckpumpe nach Anspruch 3 und wenigstens einem der Ansprüche 4 bis 8, dadurch gekennzeichnet, dass die Aufnahme (60; 160) in zumindest annähernd radialer Richtung bezüglich der Längsachse (41) des Stößels (40) beweglich ist und dass die Feder (68) auf der dem Stößel (40) abgewandten Außenseite der Aufnahme (60; 160) angreift.High-pressure pump according to claim 3 and at least one of claims 4 to 8, characterized in that the receptacle ( 60 ; 160 ) in at least approximately radial direction with respect to the longitudinal axis ( 41 ) of the plunger ( 40 ) is movable and that the spring ( 68 ) on the ram ( 40 ) facing away from the outside of the receptacle ( 60 ; 160 ) attacks. Hochdruckpumpe nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass im Stößel (40) zumindest mittelbar eine Rolle (46) drehbar gelagert ist, über die sich der Stößel (40) an der Antriebswelle (12) abstützt.High-pressure pump according to one of the preceding claims, characterized in that in the plunger ( 40 ) at least indirectly a role ( 46 ) is rotatably mounted, via which the plunger ( 40 ) on the drive shaft ( 12 ) is supported.
DE102005046670A 2005-09-29 2005-09-29 High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet Withdrawn DE102005046670A1 (en)

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DE102005046670A DE102005046670A1 (en) 2005-09-29 2005-09-29 High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet
EP06793348A EP1931875B1 (en) 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine
PCT/EP2006/066162 WO2007036423A1 (en) 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine
AT06793348T ATE460584T1 (en) 2005-09-29 2006-09-08 HIGH PRESSURE PUMP, IN PARTICULAR FOR A FUEL INJECTION DEVICE OF AN INTERNAL COMBUSTION ENGINE
DE502006006407T DE502006006407D1 (en) 2005-09-29 2006-09-08 HIGH PRESSURE PUMP, ESPECIALLY FOR A FUEL INJECTION DEVICE OF AN INTERNAL COMBUSTION ENGINE

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DE102005046670A DE102005046670A1 (en) 2005-09-29 2005-09-29 High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet

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DE502006006407T Active DE502006006407D1 (en) 2005-09-29 2006-09-08 HIGH PRESSURE PUMP, ESPECIALLY FOR A FUEL INJECTION DEVICE OF AN INTERNAL COMBUSTION ENGINE

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AT (1) ATE460584T1 (en)
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EP1931875B1 (en) 2010-03-10
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WO2007036423A1 (en) 2007-04-05
EP1931875A1 (en) 2008-06-18

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