EP1931875A1 - High pressure pump, in particular for a fuel injection device of an internal combustion engine - Google Patents

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

Info

Publication number
EP1931875A1
EP1931875A1 EP06793348A EP06793348A EP1931875A1 EP 1931875 A1 EP1931875 A1 EP 1931875A1 EP 06793348 A EP06793348 A EP 06793348A EP 06793348 A EP06793348 A EP 06793348A EP 1931875 A1 EP1931875 A1 EP 1931875A1
Authority
EP
European Patent Office
Prior art keywords
pressure pump
plunger
ball
pump
longitudinal axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06793348A
Other languages
German (de)
French (fr)
Other versions
EP1931875B1 (en
Inventor
Alfons Schoetz
Gerhard Meier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1931875A1 publication Critical patent/EP1931875A1/en
Application granted granted Critical
Publication of EP1931875B1 publication Critical patent/EP1931875B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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

Definitions

  • the invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is known from DE 199 07 311 Al.
  • 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 Pumpengehauseteils the high-pressure pump and limited in the cylinder bore a pump working space.
  • the pump piston is supported at least indirectly via a hollow cylinder-shaped plunger on the drive shaft.
  • the plunger is slidably guided in a bore of a Pumpengehauseteils in the direction of the longitudinal axis of the pump piston.
  • the inventive high-pressure pump with the features of claim 1 has the advantage that an anti-rotation of the shock ice is ensured by simple means.
  • the ball is a standard part that can be purchased inexpensively as a vendor.
  • Embodiments and developments of the inventive high-pressure pump specified Due to the design according to claim 2, a low friction in the rotation of the shock ice is achieved because there is at least at a Abstutzung the ball on the plunger rolling friction. Due to the design according to claim 3, a safe investment of the ball is achieved in the groove of the shock ice. The embodiment according to claim 4, a particularly low friction is achieved because both between the ball and the plunger and between the ball and the recording
  • FIG. 1 shows a high pressure pump for a fuel injector
  • Figure 2 Internal combustion engine in a longitudinal section, Figure 2 is a designated II in Figure 1 section of the high-pressure pump in an enlarged view according to a first exemplary embodiment, Figure 3, the high-pressure pump in a section along line III-III in Figure 2, Figure 4 a in Figure 3 with IV designated Detail in again enlarged view and Figure 5 shows the detail II of the high-pressure pump according to a second exemplary embodiment.
  • FIGS. 1 to 5 show a high-pressure pump for a fuel injection device of an internal combustion engine.
  • the high-pressure pump has a multipart pump housing 10 in which a drive shaft 12 driven in rotation by the internal combustion engine is arranged.
  • the drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12.
  • the bearings can be arranged in different parts of the Pumpengehauses 10, for example, a first bearing point in a Grundkorper 14 of Pumpengehauses 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.
  • the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam.
  • the high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12.
  • a pump housing part 22 connected to the basic body 14 is provided, which is designed as a cylinder head.
  • the pump housing part 22 has a voltage applied to an outer side of the base body 14 flange 24 and a through an opening in the base body 14 to the drive shaft 12 through protruding, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter.
  • the pump piston 20 is tightly slidably guided in a formed in the neck 26 cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30.
  • the cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged.
  • the pump chamber 30 has a in the
  • Pump housing 10 extending fuel inlet channel 32 connects to a fuel inlet, for example, a Forderpumpe.
  • a fuel inlet for example, a Forderpumpe.
  • an inlet valve 34 opening into the pump working chamber 30 is arranged.
  • the pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 with an outlet, which is connected for example to a high-pressure accumulator 110.
  • One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine.
  • an outlet valve 38 opening out of the pump working chamber 30 is arranged.
  • a plunger 40 is arranged, via which the pump piston 20 is supported at least indirectly on the cam 16 of the drive shaft 12.
  • the plunger 40 is hollow cylinder-shaped with a round outer cross-section and is slidably guided in a bore 42 of the base body 14 of the Pumpengehauses 10 in the direction of the longitudinal axis 21 of the pump piston 20.
  • the longitudinal axis 41 of the shock ice 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20.
  • a support member 44 is inserted in the drive shaft 12 facing end portion in which a roller 46 is rotatably mounted, which rolls on the cam 16 of the drive shaft 12.
  • the axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12.
  • the support element 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is mounted.
  • the pump piston 20 may be coupled to the plunger 40, at least in the direction of its longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, in which case by the return spring 52, the system of the pump piston 20 is secured to the plunger 40. It can be provided that the return spring 52, for example via a spring plate 53 at a in the
  • Diameter enlarged piston foot of the pump piston 20 engages, which is thereby held in abutment on a ram 40 of the jacket inwardly projecting flange, which in turn is held in contact with the support member 44, so that the entire composite of pump piston 20, ram 40 and support element 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.
  • groove 56 In the outer casing of the impact ice 40 at least one extending in the direction of the longitudinal axis 41 groove 56 is arranged, which preferably at least in cross section is formed approximately nikabroughformig. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the baffle 40, a ball 58 with a part of its circumference, which is fixed in the pump housing 10 in the tangential direction to the plunger 40.
  • Figures 2 to 4 is the
  • High-pressure pump according to a first exemplary embodiment shown, in which the ball 58 is guided in a receptacle 60 in the direction of the longitudinal axis 41 of the bumper 40 movable.
  • the receptacle 60 has, as shown in Figures 2 and 4, a trough-shaped recess 62 which is at least substantially prismatic in cross-section perpendicular to the longitudinal axis 41 of the baffle 40 and two opposing inclined walls, on which the ball 58 is applied in each case.
  • the ball 58 dives with a part of its circumference in the recess 62 and is thereby fixed in the tangential direction of the shock ice 40, so that the plunger 40 is secured by the ball 58 against rotation about its longitudinal axis 41.
  • the ball 58 rolls both in the groove 56 of the shock ice 40 and in the
  • the receptacle 60 is as shown in Figures 2 and 3, for example, in a at least approximately radially arranged with respect to the longitudinal axis 41 of the baffle 40 arranged bore 64 in the base body 14 of the pump housing 10.
  • the receptacle 60 is cylindrical in shape, on the tappet 40 facing the inside of the recess 62 is formed.
  • the bore 64 is closed to the outside of the main body 14 of the Pumpengehauses 10 by means of a plug 66.
  • a prestressed spring 68 between the plug 66 and the receptacle 60 is preferably a prestressed spring 68, for example a helical compression spring, clamped by the displaceable in the bore 64 receptacle 60 and thus the ball 58th is pressed towards the plunger 40.
  • an elastic sealing ring 70 for example an O-ring, may be arranged to seal the interior of the pump housing 10 to the outside. It can be provided that the plug 66 is screwed or pressed into the bore 64. In addition, it can be provided that the flange part 15 at least partially covers the bore 64 in a state assembled with the basic body 14 and thus secures the stopper 66 in the bore 64.
  • the receptacle 60 with the ball 58, the plug 66 and the spring 68 are inserted before the assembly of the Pumpengehauses 10 in the bore 64 from the outside of the base body 14 forth. When mounting the receptacle 60, it must be ensured that its recess 62 is aligned exactly parallel to the groove 56 of the baffle 40 in order to allow the lifting movement of the baffle 40 with the least possible friction.
  • the depth of the groove 56 in the plunger 40 and thus the immersion depth of the ball 58 in the groove 56 and the bias of the spring 68 determine the size of the torque against which the plunger 40 can be secured against rotation.
  • the high-pressure pump according to a second exemplary embodiment is shown, in which the basic structure of the high-pressure pump is the same as in the first exemplary embodiment, but the receptacle 160 is modified for the ball 58.
  • the receptacle 160 has on its side facing the plunger 40 a kugelkalottenformige depression 162 in which the ball 58 is rotatably mounted.
  • the receptacle 160 is in a blind bore of the Hole 64 in the base body 14 of the pump housing 10 occlusive stopper 166 slidably inserted. Between the plug 166 and the receptacle 160, the prestressed spring 68 is arranged.
  • Exemplary embodiment is that the receptacle 160 is formed simpler than the first exemplary embodiment and that the receptacle 160 can be used in any rotational positions in the pump housing 10. However, in the second exemplary embodiment, only between the ball 58 and the plunger 40 rolling friction exists, while between the ball 58 and the receptacle 160 is sliding friction.

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

Hochdruckpumpe, insbesondere für eineHigh pressure pump, especially for one
Kraftstoffeinspritzeinrichtung einer BrennkraftmaschineFuel injection device of an internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a high-pressure pump, in particular for a fuel injection device of an internal combustion engine according to the preamble of claim 1.
Eine solche Hochdruckpumpe ist durch die DE 199 07 311 Al bekannt. Diese Hochdruckpumpe weist ein Pumpengehause und wenigstens ein im Pumpengehause 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 Pumpengehauseteils der Hochdruckpumpe dicht gefuhrt und begrenzt in der Zylinderbohrung einen Pumpenarbeitsraum. Der Pumpenkolben stutzt sich zumindest mittelbar über einen hohlzylinderformigen Stößel an der Antriebswelle ab. Der Stößel ist in einer Bohrung eines Pumpengehauseteils in Richtung der Langsachse des Pumpenkolbens verschiebbar gefuhrt. Unter Umstanden kann es zu einer Verdrehung des Stoßeis um seine Langsachse in der Bohrung kommen, wodurch ein erhöhter Verschleiss des Stoßeis und/oder des Pumpengehauses sowie gegebenenfalls weiterer Teile der Hochdruckpumpe verursacht wird. Übliche Verdrehsicherungen für den Stößel sind aufwendig in der Herstellung und Montage. Vorteile der ErfindungSuch a high-pressure pump is known from DE 199 07 311 Al. 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 Pumpengehauseteils the high-pressure pump and limited in the cylinder bore a pump working space. The pump piston is supported at least indirectly via a hollow cylinder-shaped plunger on the drive shaft. The plunger is slidably guided in a bore of a Pumpengehauseteils in the direction of the longitudinal axis of the pump piston. Under certain circumstances, it may lead to a rotation of the buffing ice around its longitudinal axis in the bore, whereby increased wear of the shock ice and / or the Pumpengehauses and possibly other parts of the high-pressure pump is caused. Conventional anti-rotation for the ram are expensive to manufacture and assembly. Advantages of the invention
Die erfindungsgemaße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass eine Verdrehsicherung des Stoßeis mit einfachen Mitteln gewahrleistet ist. Bei der Kugel handelt es sich um ein Standardteil, das als Zulieferteil kostengünstig erworben werden kann.The inventive high-pressure pump with the features of claim 1 has the advantage that an anti-rotation of the shock ice is ensured by simple means. The ball is a standard part that can be purchased inexpensively as a vendor.
In den abhangigen Ansprüchen sind vorteilhafteIn the dependent claims are advantageous
Ausgestaltungen und Weiterbildungen der erfindungsgemaßen Hochdruckpumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine geringe Reibung bei der Verdrehsicherung des Stoßeis erreicht, da zumindest an einer Abstutzung der Kugel am Stößel Rollreibung vorliegt. Durch die Ausbildung gemäß Anspruch 3 wird eine sichere Anlage der Kugel in der Nut des Stoßeis 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 AufnahmeEmbodiments and developments of the inventive high-pressure pump specified. Due to the design according to claim 2, a low friction in the rotation of the shock ice is achieved because there is at least at a Abstutzung the ball on the plunger rolling friction. Due to the design according to claim 3, a safe investment of the ball is achieved in the groove of the shock ice. The embodiment according to claim 4, a particularly low friction is achieved because both between the ball and the plunger and between the ball and the recording
Rollreibung vorliegt. Durch die Ausbildung gemäß Anspruch 8 ist eine besonders einfache Montage der Aufnahme und der Kugel ermöglicht.Rolling friction is present. The embodiment according to claim 8, a particularly simple mounting of the receptacle and the ball is possible.
Zeichnungdrawing
Zwei Ausfuhrungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung naher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einerTwo exemplary embodiments of the invention are illustrated in the drawing and explained in more detail in the following description. FIG. 1 shows a high pressure pump for a fuel injector
Brennkraftmaschine in einem Längsschnitt, Figur 2 einen in Figur 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe in vergrößerter Darstellung gemäß einem ersten Ausfuhrungsbeispiel, Figur 3 die Hochdruckpumpe in einem Schnitt entlang Linie III-III in Figur 2, Figur 4 einen in Figur 3 mit IV bezeichneten Ausschnitt in nochmals vergrößerter Darstellung und Figur 5 den Ausschnitt II der Hochdruckpumpe gemäß einem zweiten Ausfuhrungsbeispiel.Internal combustion engine in a longitudinal section, Figure 2 is a designated II in Figure 1 section of the high-pressure pump in an enlarged view according to a first exemplary embodiment, Figure 3, the high-pressure pump in a section along line III-III in Figure 2, Figure 4 a in Figure 3 with IV designated Detail in again enlarged view and Figure 5 shows the detail II of the high-pressure pump according to a second exemplary embodiment.
Beschreibung der AusfuhrungsbeispieleDescription of the exemplary embodiments
In den Figuren 1 bis 5 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine dargestellt. Die Hochdruckpumpe weist ein mehrteiliges Pumpengehause 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 Pumpengehauses 10 angeordnet sein, beispielsweise kann eine erste Lagerstelle in einem Grundkorper 14 des Pumpengehauses 10 und eine zweite Lagerstelle in einem mit dem Grundkorper 14 verbundenen Flanschteil 15 angeordnet sein .FIGS. 1 to 5 show a high-pressure pump for a fuel injection device of an internal combustion engine. The high-pressure pump has a multipart pump housing 10 in which a drive shaft 12 driven in rotation by the internal combustion engine is arranged. The drive shaft 12 is rotatably supported, for example, via two bearing points spaced apart from one another in the direction of the axis of rotation 13 of the drive shaft 12. The bearings can be arranged in different parts of the Pumpengehauses 10, for example, a first bearing point in a Grundkorper 14 of Pumpengehauses 10 and a second bearing point can be arranged in a connected to the base body 14 flange 15.
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 Antriebsewelle 12 angetrieben wird. Im Bereich jedes Pumpenelements 18 ist ein mit dem Grundkorper 14 verbundenes Pumpengehauseteil 22 vorgesehen, das als Zylinderkopf ausgebildet ist. Das Pumpengehauseteil 22 weist einen an einer Außenseite des Grundkorpers 14 anliegenden Flansch 24 und einen durch eine Öffnung im Grundkorper 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 Pumpengehauseteil 22 dicht verschiebbar gefuhrt 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 imIn a lying between the two bearing areas, the drive shaft 12 at least one cam 16 or eccentrically to its axis of rotation 13 formed portion, wherein the cam 16 may be formed as a multiple cam. The high pressure pump has at least one or more arranged in the housing 10 pump elements 18, each with a pump piston 20 which is driven by the cam 16 of the drive shaft 12 in a lifting movement in at least approximately radial direction to the axis of rotation 13 of the drive shaft 12. In the region of each pump element 18, a pump housing part 22 connected to the basic body 14 is provided, which is designed as a cylinder head. The pump housing part 22 has a voltage applied to an outer side of the base body 14 flange 24 and a through an opening in the base body 14 to the drive shaft 12 through protruding, at least approximately cylindrical projection 26 with respect to the flange 24 of smaller diameter. The pump piston 20 is tightly slidably guided in a formed in the neck 26 cylinder bore 28 in the pump housing part 22 and limited with its drive shaft 12 facing away from the end face in the cylinder bore 28 a pump working space 30. The cylinder bore 28 may extend into the flange 24, in the then the pump working space 30 is arranged. The pump chamber 30 has a in the
Pumpengehause 10 verlaufenden Kraftstoffzulaufkanal 32 eine Verbindung mit einem Kraftstoffzulauf, beispielsweise einer Forderpumpe auf. An der Mundung 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 Pumpengehause 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 Mundung des Kraftstoffablaufkanals 36 in den Pumpenarbeitsraum 30 ist ein aus dem Pumpenarbeitsraum 30 öffnendes Auslassventil 38 angeordnet .Pump housing 10 extending fuel inlet channel 32 connects to a fuel inlet, for example, a Forderpumpe. At the mouth of the fuel inlet channel 32 into the pump working chamber 30, an inlet valve 34 opening into the pump working chamber 30 is arranged. The pump working chamber 30 also has a connection in the pump housing 10 extending fuel drain passage 36 with an outlet, which is connected for example to a high-pressure accumulator 110. One or preferably a plurality of injectors 120 arranged on the cylinders of the internal combustion engine are connected to the high-pressure accumulator 110, through which fuel is injected into the cylinders of the internal combustion engine. At the mouth of the fuel discharge channel 36 into the pump working chamber 30, an outlet valve 38 opening out of the pump working chamber 30 is 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 abstutzt. Der Stößel 40 ist hohlzylinderformig mit rundem Außenquerschnitt ausgebildet und ist in einer Bohrung 42 des Grundkorpers 14 des Pumpengehauses 10 in Richtung der Langsachse 21 des Pumpenkolbens 20 verschiebbar gefuhrt. Die Langsachse 41 des Stoßeis 40 ist somit zumindest im wesentlichen identisch mit der Langsachse 21 des Pumpenkolbens 20. Im Stößel 40 ist in dessen der Antriebswelle 12 zugewandtem Endbereich ein Stutzelement 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 Stutzelement 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 of the drive shaft 12, a plunger 40 is arranged, via which the pump piston 20 is supported at least indirectly on the cam 16 of the drive shaft 12. The plunger 40 is hollow cylinder-shaped with a round outer cross-section and is slidably guided in a bore 42 of the base body 14 of the Pumpengehauses 10 in the direction of the longitudinal axis 21 of the pump piston 20. The longitudinal axis 41 of the shock ice 40 is thus at least substantially identical to the longitudinal axis 21 of the pump piston 20. In the ram 40, a support member 44 is inserted in the drive shaft 12 facing end portion in which a roller 46 is rotatably mounted, which rolls on the cam 16 of the drive shaft 12. The axis of rotation 47 of the roller 46 is at least approximately parallel to the axis of rotation 13 of the drive shaft 12. The support element 44 has on its side facing the drive shaft 12 a recess 48 in which the roller 46 is mounted.
Am Stößel 40 oder am Pumpenkolben 20 greift eine vorgespannte Ruckstellfeder 52 an, die sich am Pumpengehauseteil 22 abstutzt. Durch die Ruckstellfeder 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 Langsachse 21. Alternativ kann der Pumpenkolben 20 auch nicht mit dem Stößel 40 verbunden sein, wobei dann durch die Ruckstellfeder 52 die Anlage des Pumpenkolbens 20 am Stößel 40 sichergestellt wird. Es kann vorgesehen sein, dass die Ruckstellfeder 52 beispielsweise über einen Federteller 53 an einem imOn the plunger 40 or on the pump piston 20 engages a biased return spring 52, which is supported on the pump housing part 22. By the return spring 52, the pump piston 20 and the plunger 40 are acted upon cam 16 of the drive shaft 12 out, so that the system of the roller 44 on the cam 16 and the intake shaft 12 toward the suction stroke of the pump piston 20 and at high speed of the drive shaft 12th is ensured. The pump piston 20 may be coupled to the plunger 40, at least in the direction of its longitudinal axis 21. Alternatively, the pump piston 20 may not be connected to the plunger 40, in which case by the return spring 52, the system of the pump piston 20 is secured to the plunger 40. It can be provided that the return spring 52, for example via a spring plate 53 at a in the
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 Stutzelement 44 gehalten wird, so dass der gesamte Verbund aus Pumpenkolben 20, Stößel 40 und Stutzelement 44 mit Rolle 46 zum Nocken 16 der Antriebswelle 12 hin beaufschlagt ist.Diameter enlarged piston foot of the pump piston 20 engages, which is thereby held in abutment on a ram 40 of the jacket inwardly projecting flange, which in turn is held in contact with the support member 44, so that the entire composite of pump piston 20, ram 40 and support element 44 is acted upon with roller 46 to the cam 16 of the drive shaft 12 out.
Im Außenmantel des Stoßeis 40 ist wenigstens eine in Richtung von dessen Langsachse 41 verlaufende Nut 56 angeordnet, die vorzugsweise im Querschnitt zumindest annähernd kreisabschnittformig geformt ist. In die Nut 56 greift zumindest annähernd radial zur Langsachse 41 des Stoßeis 40 eine Kugel 58 mit einem Teil ihres Umfangs ein, die im Pumpengehause 10 in tangentialer Richtung zum Stößel 40 fixiert ist. In den Figuren 2 bis 4 ist dieIn the outer casing of the impact ice 40 at least one extending in the direction of the longitudinal axis 41 groove 56 is arranged, which preferably at least in cross section is formed approximately kreisabschnittformig. In the groove 56 engages at least approximately radially to the longitudinal axis 41 of the baffle 40, a ball 58 with a part of its circumference, which is fixed in the pump housing 10 in the tangential direction to the plunger 40. In Figures 2 to 4 is the
Hochdruckpumpe gemäß einem ersten Ausfuhrungsbeispiel dargestellt, bei dem die Kugel 58 in einer Aufnahme 60 in Richtung der Langsachse 41 des Stoßeis 40 beweglich gefuhrt ist. Die Aufnahme 60 weist dabei wie in Figur 2 und 4 dargestellt eine rinnenformige Vertiefung 62 auf, die im Querschnitt senkrecht zur Langsachse 41 des Stoßeis 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 Stoßeis 40 fixiert, so dass der Stößel 40 durch die Kugel 58 gegen Verdrehen um seine Langsachse 41 gesichert ist. Bei der Hubbewegung des Stoßeis 40 zusammen mit dem Pumpenkolben 20 rollt die Kugel 58 sowohl in der Nut 56 des Stoßeis 40 als auch in derHigh-pressure pump according to a first exemplary embodiment shown, in which the ball 58 is guided in a receptacle 60 in the direction of the longitudinal axis 41 of the bumper 40 movable. The receptacle 60 has, as shown in Figures 2 and 4, a trough-shaped recess 62 which is at least substantially prismatic in cross-section perpendicular to the longitudinal axis 41 of the baffle 40 and two opposing inclined walls, on which the ball 58 is applied in each case. The ball 58 dives with a part of its circumference in the recess 62 and is thereby fixed in the tangential direction of the shock ice 40, so that the plunger 40 is secured by the ball 58 against rotation about its longitudinal axis 41. During the stroke movement of the shock ice 40 together with the pump piston 20, the ball 58 rolls both in the groove 56 of the shock ice 40 and in the
Vertiefung 62 der Aufnahme 60 ab, so dass nur eine geringe Rollreibung auftritt.Recess 62 of the receptacle 60 from, so that only a small rolling friction occurs.
Die Aufnahme 60 ist wie in den Figuren 2 und 3 dargestellt beispielsweise in einer zumindest annähernd radial bezuglich der Langsachse 41 des Stoßeis 40 angeordneten Bohrung 64 im Grundkorper 14 des Pumpengehauses 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 Grundkorpers 14 des Pumpengehauses 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 Pumpengehauses 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 Grundkorper 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 Pumpengehauses 10 in die Bohrung 64 von der Außenseite des Grundkorpers 14 her eingesetzt. Bei der Montage der Aufnahme 60 muss sichergestellt sein, dass deren Vertiefung 62 exakt parallel zur Nut 56 des Stoßeis 40 ausgerichtet ist, um die Hubbewegung des Stoßeis 40 bei geringstmoglicher Reibung zu ermöglichen.The receptacle 60 is as shown in Figures 2 and 3, for example, in a at least approximately radially arranged with respect to the longitudinal axis 41 of the baffle 40 arranged bore 64 in the base body 14 of the pump housing 10. The receptacle 60 is cylindrical in shape, on the tappet 40 facing the inside of the recess 62 is formed. The bore 64 is closed to the outside of the main body 14 of the Pumpengehauses 10 by means of a plug 66. Between the plug 66 and the receptacle 60 is preferably a prestressed spring 68, for example a helical compression spring, clamped by the displaceable in the bore 64 receptacle 60 and thus the ball 58th is pressed towards the plunger 40. In an annular groove of the plug 66, an elastic sealing ring 70, for example an O-ring, may be arranged to seal the interior of the pump housing 10 to the outside. It can be provided that the plug 66 is screwed or pressed into the bore 64. In addition, it can be provided that the flange part 15 at least partially covers the bore 64 in a state assembled with the basic body 14 and thus secures the stopper 66 in the bore 64. The receptacle 60 with the ball 58, the plug 66 and the spring 68 are inserted before the assembly of the Pumpengehauses 10 in the bore 64 from the outside of the base body 14 forth. When mounting the receptacle 60, it must be ensured that its recess 62 is aligned exactly parallel to the groove 56 of the baffle 40 in order to allow the lifting movement of the baffle 40 with 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 Große des Drehmoments gegen das der Stößel 40 gegen Verdrehung gesichert werden kann. Je großer die Tiefe der Nut 56 und damit die Eintauchtiefe der Kugel 58 in diese ist und je großer die Vorspannung der Feder 68 ist, desto großer ist das Drehmoment, gegen das der Stößel 40 gegen Verdrehung gesichert werden kann.The depth of the groove 56 in the plunger 40 and thus the immersion depth of the ball 58 in the groove 56 and the bias of the spring 68 determine the size of the torque against which the plunger 40 can be secured against rotation. The greater the depth of the groove 56 and thus the immersion depth of the ball 58 in this and the greater the bias of the spring 68, the greater the torque against which the plunger 40 can be secured against rotation.
In Figur 5 ist die Hochdruckpumpe gemäß einem zweiten Ausfuhrungsbeispiel dargestellt, bei dem der grundsatzliche Aufbau der Hochdruckpumpe gleich wie beim ersten Ausfuhrungsbeispiel ist, jedoch die Aufnahme 160 für die Kugel 58 modifiziert ist. Die Aufnahme 160 weist auf ihrer dem Stößel 40 zugewandten Seite eine kugelkalottenformige Vertiefung 162 auf, in der die Kugel 58 drehbar gelagert ist. Die Aufnahme 160 ist in eine Sackbohrung eines die Bohrung 64 im Grundkorper 14 des Pumpengehauses 10 verschließenden Stopfens 166 verschiebbar eingesetzt. Zwischen dem Stopfen 166 und der Aufnahme 160 ist die vorgespannte Feder 68 angeordnet. Vorteilhaft bei der Ausfuhrung der Hochdruckpumpe gemäß dem zweitenIn Figure 5, the high-pressure pump according to a second exemplary embodiment is shown, in which the basic structure of the high-pressure pump is the same as in the first exemplary embodiment, but the receptacle 160 is modified for the ball 58. The receptacle 160 has on its side facing the plunger 40 a kugelkalottenformige depression 162 in which the ball 58 is rotatably mounted. The receptacle 160 is in a blind bore of the Hole 64 in the base body 14 of the pump housing 10 occlusive stopper 166 slidably inserted. Between the plug 166 and the receptacle 160, the prestressed spring 68 is arranged. Advantageous in the execution of the high pressure pump according to the second
Ausfuhrungsbeispiel ist, dass die Aufnahme 160 einfacher ausgebildet ist als beim ersten Ausfuhrungsbeispiel und dass die Aufnahme 160 in beliebigen Drehstellungen in das Pumpengehause 10 eingesetzt werden kann. Allerdings ist beim zweiten Ausfuhrungsbeispiel nur zwischen der Kugel 58 und dem Stößel 40 Rollreibung vorhanden, wahrend zwischen der Kugel 58 und der Aufnahme 160 Gleitreibung vorliegt.Exemplary embodiment is that the receptacle 160 is formed simpler than the first exemplary embodiment and that the receptacle 160 can be used in any rotational positions in the pump housing 10. However, in the second exemplary embodiment, only between the ball 58 and the plunger 40 rolling friction exists, while between the ball 58 and the receptacle 160 is sliding friction.
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 befullt, wobei das Auslassventil 38 geschlossen ist. Beim Forderhub des Pumpenkolbens 20, bei dem sich dieser radial nach aussen bewegt, wird durch den Pumpenkolben 20 Kraftstoff unterDuring the suction stroke of the pump piston 20, in which this moves radially inward, the pump chamber 30 is filled by the fuel inlet channel 32 with the intake valve 34 open with fuel, the exhaust valve 38 is closed. When Forderhub the pump piston 20, in which this moves radially outward, 20 is under the fuel pump by the pump piston
Hochdruck durch den Kraftstoffablaufkanal 36 bei geöffnetem Auslassventil 38 zum Hochdruckspeicher 110 gefordert, wobei das Einlassventil 34 geschlossen ist. High pressure through the fuel drain passage 36 with the exhaust valve 38 open to the high-pressure accumulator 110 required, the inlet valve 34 is closed.

Claims

29.08.2005 Gu/KliROBERT BOSCH GMBH, 70442 StuttgartAnsprüche 29.08.2005 Gu / KliROBERT BOSCH GMBH, 70442 Stuttgart claims
1. Hochdruckpumpe, insbesondere für eine1. high-pressure pump, in particular for a
Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine, mit einem Pumpengehause (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 Pumpengehauses (22) verschiebbar gefuhrt ist und in dieser einen Pumpenarbeitsraum (30) begrenzt, wobei sich der Pumpenkolben (20) zumindest mittelbar über einen hohlzylinderformigen Stößel (40) an der Antriebswelle (12) abstutzt, wobei der Stößel (40) in einer Bohrung (42) eines Teils des Pumpengehauses (14) in Richtung der Langsachse (21) des Pumpenkolbens (20) verschiebbar gefuhrt ist, dadurch gekennzeichnet, dass der Stößel (40) in seinem Außenmantel eine in Richtung seiner Langsachse (41) verlaufende Nut (56) aufweist, in die zumindest annähernd radial zur Langsachse (41) des Stoßeis (40) eine zumindest mittelbar in einem Teil des Pumpengehauses (14) in tangentialer Richtung zum Stößel (40) fixierte Kugel (58) zur Verdrehsicherung des Stoßeis (40) eingreift.A fuel injection device of an internal combustion engine, comprising a pump housing (10, 14, 22) having at least one pump element (18) which has a pump piston (20) driven by a drive shaft (12) in a stroke movement, in a cylinder bore (28) of a part the Pumpengehauses (22) is slidably guided and limited in this a pump working space (30), wherein the pump piston (20) at least indirectly via a hollow cylindrical tappet (40) on the drive shaft (12), wherein the plunger (40) in a Bore (42) of a part of the Pumpengehauses (14) in the direction of the longitudinal axis (21) of the pump piston (20) is slidably guided, characterized in that the plunger (40) in its outer jacket in the direction of its longitudinal axis (41) extending groove ( 56), in which at least approximately radially to the longitudinal axis (41) of the bumper ice (40) at least indirectly in a part of the Pumpengehauses (14) in a tangential direction to the plunger ( 40) fixed ball (58) to prevent rotation of the shock ice (40) engages.
2. Hochdruckpumpe nach Anspruch 1, dadurch gekennzeichnet, dass zumindest zwischen der Kugel (58) und dem Stößel (40) Rollreibung vorliegt.2. High-pressure pump according to claim 1, characterized in that there is at least between the ball (58) and the plunger (40) rolling friction.
3. Hochdruckpumpe nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kugel (58) zumindest mittelbar durch eine vorgespannte Feder (68) in die Nut (56) des Stoßeis (40) gepresst wird.3. High-pressure pump according to claim 1 or 2, characterized in that the ball (58) at least indirectly is pressed by a prestressed spring (68) into the groove (56) of the bumper (40).
4. Hochdruckpumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Kugel (58) in einer im4. High-pressure pump according to claim 2 or 3, characterized in that the ball (58) in a in
Pumpengehauseteil (14) angeordneten Aufnahme (60) in Richtung der Langsachse (41) des Stoßeis (40) beweglich gefuhrt ist.Pump housing part (14) arranged receiving (60) in the direction of the longitudinal axis (41) of the bumper (40) is guided movably.
5. Hochdruckpumpe nach Anspruch 4, dadurch gekennzeichnet, dass die Fuhrung (62) für die Kugel (58) in der Aufnahme (60) im Querschnitt senkrecht zur Langsachse (41) des Stoßeis (40) zumindest annähernd prismatisch ausgebildet ist.5. High-pressure pump according to claim 4, characterized in that the guide (62) for the ball (58) in the receptacle (60) in cross-section perpendicular to the longitudinal axis (41) of the bumper (40) is at least approximately prismatic.
6. Hochdruckpumpe nach Anspruch 2 oder 3, dadurch gekennzeichnet, dass die Kugel (58) in einer im Pumpengehauseteil (14) angeordneten Aufnahme (160) drehbar gelagert ist.6. 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.
7. Hochdruckpumpe nach Anspruch 6, dadurch gekennzeichnet, dass die Aufnahme (160) eine zumindest annähernd kugelkalottenformige Vertiefung (162) aufweist, in der die Kugel (58) gelagert ist.7. High-pressure pump according to claim 6, characterized in that the receptacle (160) has an at least approximately kugelkalottenformige depression (162) in which the ball (58) is mounted.
8. Hochdruckpumpe nach einem der Ansprüche 4 bis 7, dadurch gekennzeichnet, dass die Aufnahme (60; 160) in einer Bohrung8. High-pressure pump according to one of claims 4 to 7, characterized in that the receptacle (60; 160) in a bore
(64) im Pumpengehauseteil (14) eingesetzt ist, vorzugsweise von einer der Bohrung (42), in der der Stößel (40) gefuhrt ist, abgewandten Außenseite des Pumpengehauseteils (14) her .(64) in the pump housing part (14) is inserted, preferably from one of the bore (42) in which the plunger (40) is guided, facing away from the outside of the pump housing part (14).
9. Hochdruckpumpe nach Anspruch 3 und wenigstens einem der Ansprüche 4 bis 8, dadurch gekennzeichnet, dass die Aufnahme (60; 160) in zumindest annähernd radialer Richtung bezuglich der Langsachse (41) des Stoßeis (40) beweglich ist und dass die Feder (68) auf der dem Stößel (40) abgewandten Außenseite der Aufnahme (60:160) angreift.9. 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 bumper (40) movable and that the spring (68) acts on the outer side of the receptacle (60: 160) facing away from the plunger (40).
10. 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) abstutzt. 10. High-pressure pump according to one of the preceding claims, characterized in that in the plunger (40) at least indirectly, a roller (46) is rotatably mounted, via which the plunger (40) on the drive shaft (12).
EP06793348A 2005-09-29 2006-09-08 High pressure pump, in particular for a fuel injection device of an internal combustion engine Not-in-force EP1931875B1 (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
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

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EP1931875B1 EP1931875B1 (en) 2010-03-10

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AT (1) ATE460584T1 (en)
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DE502006006407D1 (en) 2010-04-22
DE102005046670A1 (en) 2007-04-05

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