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EP1552145B1 - High pressure pump, especially for a fuel injection device in an internal combustion engine - Google Patents

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

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Publication number
EP1552145B1
EP1552145B1 EP03807731A EP03807731A EP1552145B1 EP 1552145 B1 EP1552145 B1 EP 1552145B1 EP 03807731 A EP03807731 A EP 03807731A EP 03807731 A EP03807731 A EP 03807731A EP 1552145 B1 EP1552145 B1 EP 1552145B1
Authority
EP
European Patent Office
Prior art keywords
pressure
casing
pump
bores
pressure pump
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.)
Expired - Lifetime
Application number
EP03807731A
Other languages
German (de)
French (fr)
Other versions
EP1552145A1 (en
Inventor
Burkhard Boos
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1552145A1 publication Critical patent/EP1552145A1/en
Application granted granted Critical
Publication of EP1552145B1 publication Critical patent/EP1552145B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F02M59/04—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F02M59/06—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 special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps with cylinders arranged radially to driving shaft, e.g. in V or star arrangement
    • 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
    • F02M59/08—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 two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
    • 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
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/007—Cylinder heads
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

  • the invention relates to a high-pressure pump, in particular for a fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a high-pressure pump is through the DE 198 02 476 A1 known.
  • This high-pressure pump has a pump housing, in which a plurality of pump elements are arranged.
  • the pump elements convey fuel via a high-pressure channel system to a common high-pressure connection.
  • the pump housing of the high-pressure pump is formed in one piece and the high-pressure channel system has through the pump housing extending high pressure bores, which open into one another and thereby form intersections.
  • high pressures such as are required for fuel injectors to achieve high performance and low emissions of pollutants in internal combustion engines, resulting in high loads for the pump housing.
  • Such a high pressure pump is also from the EP 1 188 926 A2 known.
  • the subject matter of claim 1 is delimited in two-part form with respect to this document.
  • intersections of the high-pressure bores result in voltage spikes in the pump housing, according to which the pump housing must be dimensioned and designed with regard to the material. In this case, a complex hardening treatment of the pump housing is required. The production of the high-pressure pump is expensive for these reasons.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that the housing body is less stressed because of the lack of intersections and thus can be made of a less expensive material and in a simpler way, making a total of the production of the high-pressure pump is less expensive. Holes with intersections are usually present in the housing covers, so that they must be made of material with appropriate strength anyway and there resulting further intersections of high-pressure holes lead to no increased effort.
  • FIG. 1 a high-pressure pump in a longitudinal section
  • FIG. 2 the high pressure pump in a cross section along line II-II in FIG. 1 according to a first embodiment
  • FIG. 3 the high pressure pump in cross section according to a second embodiment.
  • a high-pressure pump is shown, which is provided in particular for a fuel injection device for an internal combustion engine, for example a motor vehicle. Due to the high-pressure pump while fuel is pumped under high pressure of up to 2000, For example, in a memory, is taken from the fuel for injection to the internal combustion engine.
  • the high-pressure pump has a multipart pump housing, which has a housing body 10, a flange part 12 and housing cover 10 connected to the housing body 10.
  • the pump housing several, for example, three circumferentially uniformly distributed pump elements 16 are arranged.
  • a drive shaft 18 is rotatably mounted, through which the pump elements 16 are driven.
  • the drive shaft 18 is rotatably supported about a bearing 19 in the housing body 10 and a bearing point 22 in the flange 12 about an axis 19 and is driven in a manner not shown by the internal combustion engine.
  • the drive shaft 18 has an eccentric portion 24 on which a cam ring 26 is mounted.
  • the pump elements 16 each have a pump piston 28 which is slidably guided in an approximately at least approximately radially to the drive shaft 18 extending cylinder bore 30.
  • the cylinder bores 30 of the pump elements 16 may be formed in the housing body 10 or in the housing covers 14. For each pump element 16, a housing cover 14, which covers this radially with respect to the axis of rotation 19 of the drive shaft 18, is provided.
  • each pump element 16 is supported with its piston foot 29 on the cam ring 26, wherein the piston foot 29 by a spring 32 which is supported on the one hand on the housing body 10 or the housing cover 14 and on the other hand on the piston foot 29, is held in contact with the cam ring 26 ,
  • a pump working space 34 is limited in the cylinder bore 30 with its end face.
  • the pump working chamber 34 can be connected to a fuel inlet channel 38 in which low pressure prevails by means of an inlet valve 36 which opens into the pump working chamber 34.
  • an outlet valve 40 which opens toward the store via a high-pressure passage system which extends in the housing body 10 and in the housing covers 14 and which is explained in more detail below.
  • the respective pump piston 28 When the respective pump piston 28 moves radially inward, it performs a suction stroke, wherein the respective inlet valve 36 is opened, so that fuel flows through the fuel inlet passage 38 into the respective pump working chamber 34, while the respective outlet valve 40 is closed.
  • the respective pump piston 28 moves radially outward, it performs a delivery stroke, wherein the respective inlet valve 36 is closed and the fuel compressed by the pump piston 28 passes through the open outlet valve 40 under high pressure via the high-pressure channel system in the memory.
  • a high-pressure port 42 is arranged, to which a high pressure line leading to the memory 44 is connected.
  • the pumped by the pump elements 16 fuel is passed through the high-pressure channel system for common to all pump elements 16 high-pressure port 42.
  • the high-pressure port 42 may be arranged with any orientation on the housing cover 14a.
  • the respective inlet valve 36 and / or the respective outlet valve 40 of each pump element 16 can be arranged in the respective housing cover 14a, b, c.
  • the following is based on the FIG. 2 the high-pressure channel system in the housing body 10 and in the housing covers 14a, b, c explained in more detail.
  • the two housing covers 14b, c where not the high-pressure port 42 is arranged, leads to the respective outlet valve 40 then each one Bore 50 to the housing body 10 down from.
  • the holes 50 extend at least approximately radially to the axis of rotation 19 of the drive shaft 18.
  • the mouths of the holes 50 may be widened in diameter, for example conical or spherical.
  • the housing cover 14a, b, c and the housing body 10 have mutually facing, at least approximately flat surfaces 11 and 15, with which they rest against each other.
  • high-pressure bores 52 and 54 which each connect to the bores 50 of the two housing cover 14b, c and lead to the housing cover 14a, on which the common high-pressure port 42 is arranged.
  • c facing surfaces 15 of the housing body 10 each have a recess 56 is introduced, at the at least approximately flat bottom 57, the high-pressure bore 52 and 54 opens.
  • the mouth of the high-pressure bore 52 or 54 at the bottom 57 of the recess 56 is preferably rounded in each case. This can be done with a form drill, which can be attached to the flat bottom 57 of the recess 56.
  • the depressions 56 each have a larger cross-section than the high-pressure bores 52, 54.
  • a respective high pressure bores 52,54 surrounding sealing ring 58 is inserted, through which the transition from the bore 50 in the housing cover 14b, c is sealed to the high pressure bore 52 and 54 in the housing part 10.
  • a recess 60 is introduced into the housing cover 14a facing surface 11 of the housing body 10, which has an at least approximately flat bottom 61.
  • the two high pressure bores 52 and 54 in the housing body 10 open into the recess 60 at a distance from each other.
  • the depression 60 is thus larger in its cross section than the sum of the diameters of the two high-pressure bores 52, 54.
  • the mouth of the high pressure bores 52,54 at the bottom 61 of the Recess 60 is preferably rounded in each case, which in turn can be easily produced by means of a form drill which can be attached to the flat bottom 61 of the depression 60.
  • a high-pressure bores 52,54 surrounding sealing ring 62 is inserted.
  • a bore 50 which is arranged at least approximately centrally relative to the depression 60, which leads to the common high-pressure connection 42, is introduced into the housing cover 14a.
  • the bore 50 extends at least approximately radially to the axis of rotation 19 of the drive shaft 18.
  • the recess 60 facing the mouth of the bore 50 may be widened in diameter, for example, conical or rounded.
  • the transition from the high-pressure bores 52, 54 in the housing body 10 to the bore 50 in the housing cover 14 a is sealed by the sealing ring 62.
  • the bore 50 in the housing cover 14a and the outlet of the outlet cover 40 arranged in the housing cover 14a lead to the common high pressure port 42.
  • the high pressure bores 52,54 extend in the housing body 10 without intersections and are merged in the recess 60 in the region of the transition from the housing body 10 to the housing cover 14a ,
  • the stress on the housing body 10 is thus kept so low that it can be made of inexpensive metal with sufficient strength and without special hardening treatment such as steel or at lower pressure generated by the pump elements 16 and light metal such as aluminum.
  • the pressure generated by the high-pressure pump can be increased while still ensuring a sufficient durability of the housing body 10.
  • the housing cover 14 a, b, c have intersections, at the transition of the flow of the respective exhaust valve 40 into the bore 50 and are made of metal with a correspondingly higher strength than the housing body 10 made, for example, hardened steel.
  • FIG. 3 is the high-pressure pump according to a second embodiment shown, in which the structure is substantially the same as in the first embodiment and to which only the deviating features are explained below.
  • the housing cover 14a facing surface 11 of the housing body 10 while two separate recesses 160 are introduced, wherein in each recess 160, a high-pressure bore 52 and 54 opens.
  • the recesses 160 each have an at least approximately flat bottom 161, and the mouth of the high-pressure bore 52 or 54 in the respective recess 160 is preferably rounded.
  • two bores 152,154 are introduced, which continue the high-pressure bores 52,54 to the common high pressure port 42 back.
  • each recess 160 is a respective high-pressure bore 52 and 54 surrounding sealing ring 162 is used to seal the transition from the housing body 10 to the housing cover 14a. Also in the second embodiment thus run the high pressure bores 52,54 in the housing body 10 without intersections and there are only in the housing cover 14a intersections.

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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)
  • Reciprocating Pumps (AREA)

Description

Stand der TechnikState of the art

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

Eine solche Hochdruckpumpe ist durch die DE 198 02 476 A1 bekannt. Diese Hochdruckpumpe weist ein Pumpengehäuse auf, in dem mehrere Pumpenelemente angeordnet sind. Durch die Pumpenelemente wird Kraftstoff über ein Hochdruckkanalsystem zu einem gemeinsamen Hochdruckanschluss gefördert. Das Pumpengehäuse der Hochdruckpumpe ist dabei einteilig ausgebildet und das Hochdruckkanalsystem weist durch das Pumpengehäuse verlaufende Hochdruckbohrungen auf, die ineinander münden und dabei Verschneidungen bilden. Bei hohen Drücken, wie sie für Kraftstoffeinspritzeinrichtungen zur Erzielung hoher Leistung und geringer Schadstoffemissionen bei Brennkraftmaschinen erfoderlich sind, ergeben hohe Belastungen für das Pumpengehäuse.Such a high-pressure pump is through the DE 198 02 476 A1 known. This high-pressure pump has a pump housing, in which a plurality of pump elements are arranged. The pump elements convey fuel via a high-pressure channel system to a common high-pressure connection. The pump housing of the high-pressure pump is formed in one piece and the high-pressure channel system has through the pump housing extending high pressure bores, which open into one another and thereby form intersections. At high pressures, such as are required for fuel injectors to achieve high performance and low emissions of pollutants in internal combustion engines, resulting in high loads for the pump housing.

Eine derartige Hochdruckpumpe ist ebenfalls aus der EP 1 188 926 A2 bekannt. Der Gegenstand des Anspruchs 1 ist in zweiteiliger Form gegenüber dieser Druckschrift abgegrenzt.Such a high pressure pump is also from the EP 1 188 926 A2 known. The subject matter of claim 1 is delimited in two-part form with respect to this document.

Durch die Verschneidungen der Hochdruckbohrungen ergeben sich Spannungsspitzen im Pumpengehäuse, entsprechend denen das Pumpengehäuse dimensioniert und hinsichtlich des Werkstoffs ausgelegt werden muss. Hierbei ist auch eine aufwendige Härtebehandlung des Pumpengehäuses erforderlich. Die Fertigung der Hochdruckpumpe ist aus diesen Gründen teuer.The intersections of the high-pressure bores result in voltage spikes in the pump housing, according to which the pump housing must be dimensioned and designed with regard to the material. In this case, a complex hardening treatment of the pump housing is required. The production of the high-pressure pump is expensive for these reasons.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass der Gehäusekörper wegen der fehlenden Verschneidungen weniger stark beansprucht wird und somit aus einem kostengünstigeren Werkstoff und auf einfachere Weise hergestellt werden kann, wodurch insgesamt die Herstellung der Hochdruckpumpe kostengünstiger ist. In den Gehäusedeckeln sind üblicherweise Bohrungen mit Verschneidungen vorhanden, so dass diese ohnehin aus Material mit entsprechender Festigkeit hergestellt werden müssen und dort entstehende weitere Verschneidungen der Hochdruckbohrungen zu keinem erhöhten Aufwand führen.The high pressure pump according to the invention with the features of claim 1 has the advantage that the housing body is less stressed because of the lack of intersections and thus can be made of a less expensive material and in a simpler way, making a total of the production of the high-pressure pump is less expensive. Holes with intersections are usually present in the housing covers, so that they must be made of material with appropriate strength anyway and there resulting further intersections of high-pressure holes lead to no increased effort.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemässen Hochdruckpumpe angegeben.In the dependent claims advantageous refinements and developments of the novel high-pressure pump are given.

Zeichnungdrawing

Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Hochdruckpumpe in einem Längsschnitt, Figur 2 die Hochdruckpumpe in einem Querschnitt entlang Linie II-II in Figur 1 gemäss einem ersten Ausführungsbeispiel und Figur 3 die Hochdruckpumpe im Querschnitt 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 FIG. 1 a high-pressure pump in a longitudinal section, FIG. 2 the high pressure pump in a cross section along line II-II in FIG. 1 according to a first embodiment and FIG. 3 the high pressure pump in cross section according to a second embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In den Figuren 1 bis 3 ist eine Hochdruckpumpe dargestellt, die insbesondere für eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs vorgesehen ist. Durch die Hochdruckpumpe wird dabei Kraftstoff unter Hochdruck von bis zu 2000 bar gefördert, beispielsweise in einen Speicher, aus dem Kraftstoff zur Einspritzung an der Brennkraftmaschine entnommen wird. Die Hochdruckpumpe weist ein mehrteiliges Pumpengehäuse auf, das einen Gehäusekörper 10, ein Flanschteil 12 und mit dem Gehäusekörper 10 verbundene Gehäusedeckel 14 aufweist. Im Pumpengehäuse sind mehrere, beispielsweise drei über den Umfang gleichmässig verteilte Pumpenelemente 16 angeordnet. Im Gehäusekörper 10 und dem Flanschteil 12 ist eine Antriebswelle 18 drehbar gelagert angeordnet, durch die die Pumpenelemente 16 angetrieben werden. Die Antriebswelle 18 ist über eine Lagerstelle 20 im Gehäusekörper 10 und über eine Lagerstelle 22 im Flanschteil 12 um eine Achse 19 drehbar gelagert und wird in nicht dargestellter Weise durch die Brennkraftmaschine angetrieben. Die Antriebswelle 18 weist einen Exzenterabschnitt 24 auf, auf dem ein Hubring 26 gelagert ist. Die Pumpenelemente 16 weisen jeweils einen Pumpenkolben 28 auf, der in einer zumindest annähernd radial zur Antriebswelle 18 verlaufenden Zylinderbohrung 30 verschiebbar dicht geführt ist. Die Zylinderbohrungen 30 der Pumpenelemente 16 können im Gehäusekörper 10 oder in den Gehäusedeckeln 14 ausgebildet sein. Für jedes Pumpenelement 16 ist ein dieses radial bezüglich der Drehachse 19 der Antriebswelle 18 nach aussen abdeckender Gehäusedeckel 14 vorgesehen. Der Pumpenkolben 28 jedes Pumpenelements 16 stützt sich mit seinem Kolbenfuß 29 am Hubring 26 ab, wobei der Kolbenfuss 29 durch eine Feder 32, die sich einerseits am Gehäusekörper 10 oder dem Gehäusedeckel 14 und andererseits am Kolbenfuss 29 abstützt, in Anlage am Hubring 26 gehalten wird.In the FIGS. 1 to 3 a high-pressure pump is shown, which is provided in particular for a fuel injection device for an internal combustion engine, for example a motor vehicle. Due to the high-pressure pump while fuel is pumped under high pressure of up to 2000, For example, in a memory, is taken from the fuel for injection to the internal combustion engine. The high-pressure pump has a multipart pump housing, which has a housing body 10, a flange part 12 and housing cover 10 connected to the housing body 10. In the pump housing several, for example, three circumferentially uniformly distributed pump elements 16 are arranged. In the housing body 10 and the flange 12, a drive shaft 18 is rotatably mounted, through which the pump elements 16 are driven. The drive shaft 18 is rotatably supported about a bearing 19 in the housing body 10 and a bearing point 22 in the flange 12 about an axis 19 and is driven in a manner not shown by the internal combustion engine. The drive shaft 18 has an eccentric portion 24 on which a cam ring 26 is mounted. The pump elements 16 each have a pump piston 28 which is slidably guided in an approximately at least approximately radially to the drive shaft 18 extending cylinder bore 30. The cylinder bores 30 of the pump elements 16 may be formed in the housing body 10 or in the housing covers 14. For each pump element 16, a housing cover 14, which covers this radially with respect to the axis of rotation 19 of the drive shaft 18, is provided. The pump piston 28 of each pump element 16 is supported with its piston foot 29 on the cam ring 26, wherein the piston foot 29 by a spring 32 which is supported on the one hand on the housing body 10 or the housing cover 14 and on the other hand on the piston foot 29, is held in contact with the cam ring 26 ,

Durch den Pumpenkolben 28 jedes Pumpenelements 16 wird in der Zylinderbohrung 30 mit seiner Stirnseite jeweils ein Pumpenarbeitsraum 34 begrenzt. Der Pumpenarbeitsraum 34 ist durch ein in den Pumpenarbeitsraum 34 öffnendes Einlassventil 36 mit einem Kraftstoffzulaufkanal 38 verbindbar ist, in dem Niederdruck herrscht. Der Pumpenarbeitsraum 34 ist außerdem durch ein zum Speicher hin öffnendes Auslassventil 40 über ein im Gehäusekörper 10 und in den Gehäusedeckeln 14 verlaufendes, nachfolgend näher erläutertes Hochdruckkanalsystem mit dem Speicher verbindbar. Bei der Rotation der Antriebswelle 18 werden die Pumpenkolben 28 über den Exzenterabschnitt 24 und den Hubring 26 in einer Hubbewegung angetrieben. Wenn sich der jeweilige Pumpenkolben 28 radial nach innen bewegt, so führt dieser einen Saughub aus, wobei das jeweilige Einlassventil 36 geöffnet ist, so dass Kraftstoff über den Kraftstoffzulaufkanal 38 in den jeweiligen Pumpenarbeitsraum 34 einströmt, während das jeweilige Auslassventil 40 geschlossen ist. Wenn sich der jeweilige Pumpenkolben 28 radial nach aussen bewegt, so führt dieser einen Förderhub aus, wobei das jeweilige Einlassventil 36 geschlossen ist und der vom Pumpenkolben 28 verdichtete Kraftstoff durch das geöffnete Auslassventil 40 unter hohem Druck über das Hochdruckkanalsystem in den Speicher gelangt.By the pump piston 28 of each pump element 16 in each case a pump working space 34 is limited in the cylinder bore 30 with its end face. The pump working chamber 34 can be connected to a fuel inlet channel 38 in which low pressure prevails by means of an inlet valve 36 which opens into the pump working chamber 34. Of the Pump work space 34 is also connectable to the store by means of an outlet valve 40 which opens toward the store via a high-pressure passage system which extends in the housing body 10 and in the housing covers 14 and which is explained in more detail below. Upon rotation of the drive shaft 18, the pump piston 28 are driven via the eccentric portion 24 and the cam ring 26 in a lifting movement. When the respective pump piston 28 moves radially inward, it performs a suction stroke, wherein the respective inlet valve 36 is opened, so that fuel flows through the fuel inlet passage 38 into the respective pump working chamber 34, while the respective outlet valve 40 is closed. When the respective pump piston 28 moves radially outward, it performs a delivery stroke, wherein the respective inlet valve 36 is closed and the fuel compressed by the pump piston 28 passes through the open outlet valve 40 under high pressure via the high-pressure channel system in the memory.

An einem Gehäusedeckel 14a ist ein Hochdruckanschluss 42 angeordnet, an dem eine zum Speicher führende Hochdruckleitung 44 angeschlossen ist. Der von den Pumpenelementen 16 geförderte Kraftstoff wird über das Hochdruckkanalsystem zum für alle Pumpenelemente 16 gemeinsamen Hochdruckanschluss 42 geleitet. Der Hochdruckanschluss 42 kann mit beliebiger Orientierung am Gehäusedeckel 14a angeordnet sein. Das jeweilige Einlassventil 36 und/oder das jeweilige Auslassventil 40 eines jeden Pumpenelements 16 kann im jeweiligen Gehäusedeckel 14a,b,c angeordnet sein.On a housing cover 14a, a high-pressure port 42 is arranged, to which a high pressure line leading to the memory 44 is connected. The pumped by the pump elements 16 fuel is passed through the high-pressure channel system for common to all pump elements 16 high-pressure port 42. The high-pressure port 42 may be arranged with any orientation on the housing cover 14a. The respective inlet valve 36 and / or the respective outlet valve 40 of each pump element 16 can be arranged in the respective housing cover 14a, b, c.

Nachfolgend wird anhand der Figur 2 das Hochdruckkanalsystem im Gehäusekörper 10 und in den Gehäusedeckeln 14a,b,c näher erläutert. In den beiden Gehäusedeckeln 14b,c, an denen nicht der Hochdruckanschluss 42 angeordnet ist, führt an das jeweilige Auslassventil 40 anschliessend jeweils eine Bohrung 50 zum Gehäusekörper 10 hin ab. Die Bohrungen 50 verlaufen zumindest annähernd radial zur Drehachse 19 der Antriebswelle 18. Die Mündungen der Bohrungen 50 können im Durchmesser erweitert sein, beispielsweise konisch oder kugelförmig. Die Gehäusedeckel 14a,b,c und der Gehäusekörper 10 weisen einander zugewandte, zumindest annähernd ebene Flächen 11 bzw. 15 auf, mit denen diese aneinander anliegen. Im Gehäusekörper 10 verlaufen Hochdruckbohrungen 52 und 54, die sich jeweils an die Bohrungen 50 der beiden Gehäusedeckel 14b,c anschliessen und die zu dem Gehäusedeckel 14a führen, an dem der gemeinsame Hochdruckanschluss 42 angeordnet ist. In den den Gehäusedeckeln 14b,c zugewandten Flächen 15 des Gehäusekörpers 10 ist jeweils eine Vertiefung 56 eingebracht, an deren zumindest annähernd ebenem Boden 57 die Hochdruckbohrung 52 bzw. 54 mündet. Die Mündung der Hochdruckbohrung 52 bzw. 54 am Boden 57 der Vertiefung 56 ist jeweils vorzugsweise verrundet. Dies kann mit einem Formbohrer erfolgen, der am ebenen Boden 57 der Vertiefung 56 angesetzt werden kann. Die Vertiefungen 56 weisen jeweils einen grösseren Querschnitt auf als die Hochdruckbohrungen 52,54. In die Vertiefungen 56 ist jeweils ein die Hochdruckbohrungen 52,54 umgebender Dichtring 58 eingesetzt, durch den der Übergang von der Bohrung 50 im Gehäusedeckel 14b,c zur Hochdruckbohrung 52 bzw. 54 im Gehäuseteil 10 abgedichtet wird.The following is based on the FIG. 2 the high-pressure channel system in the housing body 10 and in the housing covers 14a, b, c explained in more detail. In the two housing covers 14b, c, where not the high-pressure port 42 is arranged, leads to the respective outlet valve 40 then each one Bore 50 to the housing body 10 down from. The holes 50 extend at least approximately radially to the axis of rotation 19 of the drive shaft 18. The mouths of the holes 50 may be widened in diameter, for example conical or spherical. The housing cover 14a, b, c and the housing body 10 have mutually facing, at least approximately flat surfaces 11 and 15, with which they rest against each other. In the housing body 10 are high-pressure bores 52 and 54, which each connect to the bores 50 of the two housing cover 14b, c and lead to the housing cover 14a, on which the common high-pressure port 42 is arranged. In the housing covers 14b, c facing surfaces 15 of the housing body 10 each have a recess 56 is introduced, at the at least approximately flat bottom 57, the high-pressure bore 52 and 54 opens. The mouth of the high-pressure bore 52 or 54 at the bottom 57 of the recess 56 is preferably rounded in each case. This can be done with a form drill, which can be attached to the flat bottom 57 of the recess 56. The depressions 56 each have a larger cross-section than the high-pressure bores 52, 54. In the recesses 56 a respective high pressure bores 52,54 surrounding sealing ring 58 is inserted, through which the transition from the bore 50 in the housing cover 14b, c is sealed to the high pressure bore 52 and 54 in the housing part 10.

Bei dem in Figur 2 dargestellten ersten Ausführungsbeispiel ist in die dem Gehäusedeckel 14a zugewandten Fläche 11 des Gehäusekörpers 10 eine Vertiefung 60 eingebracht, die einen zumindest annähernd ebenen Boden 61 aufweist. Die beiden Hochdruckbohrungen 52 und 54 im Gehäusekörper 10 münden in die Vertiefung 60 mit Abstand voneinander. Die Vertiefung 60 ist in ihrem Querschnitt somit grösser ausgebildet als die Summe der Durchmesser der beiden Hochdruckbohrungen 52,54. Die Mündung der Hochdruckbohrungen 52,54 am Boden 61 der Vertiefung 60 ist vorzugsweise jeweils verrundet, was wiederum mittels eines am ebenen Boden 61 der Vertiefung 60 ansetzbaren Formbohrers einfach hergestellt werden kann. In die Vertiefung 60 ist ein die Hochdruckbohrungen 52,54 umgebender Dichtring 62 eingesetzt. Im Gehäusedeckel 14a ist eine zumindest annähernd zentral zur Vertiefung 60 angeordnete Bohrung 50 eingebracht, die zum gemeinsamen Hochdruckanschluss 42 führt. Die Bohrung 50 verläuft zumindest annähernd radial zur Drehachse 19 der Antriebswelle 18. Die der Vertiefung 60 zugewandte Mündung der Bohrung 50 kann im Durchmesser erweitert sein, beispielsweise konisch oder gerundet. Durch den Dichtring 62 wird der Übergang von den Hochdruckbohrungen 52,54 im Gehäusekörper 10 zur Bohrung 50 im Gehäusedeckel 14a abgedichtet. Die Bohrung 50 im Gehäusedeckel 14a und der Ablauf des im Gehäusedeckel 14a angeordneten Auslassventils 40 führen zum gemeinsamen Hochdruckanschluss 42. Die Hochdruckbohrungen 52,54 verlaufen im Gehäusekörper 10 ohne Verschneidungen und sind in der Vertiefung 60 im Bereich des Übergangs vom Gehäusekörper 10 zum Gehäusedeckel 14a zusammengeführt. Die Beanspruchung des Gehäusekörpers 10 wird dadurch so gering gehalten, dass dieser aus kostengünstigem Metall mit ausreichender Festigkeit und ohne spezielle Härtebehandlung wie beispielsweise Stahl oder bei geringerem von den Pumpenelementen 16 erzeugtem Druck auch aus Leichtmetall wie beispielsweise Aluminium hergestellt werden kann. Alternativ kann bei Verwendung eines Metalls mit hoher Festigkeit, wie sie bei einem Verlauf der Hochdruckbohrungen mit Verschneidungen erforderlich ist, der durch die Hochdruckpumpe erzeugte Druck gesteigert werden und trotzdem eine ausreichende Haltbarkeit des Gehäusekörpers 10 sichergestellt sein. Die Gehäusedeckel 14a,b,c weisen Verschneidungen auf, beim Übergang des Ablaufs des jeweiligen Auslassventils 40 in die Bohrung 50 und sind aus Metall mit entsprechend höherer Festigkeit als der Gehäusekörper 10 hergestellt, beispielsweise aus gehärtetem Stahl.At the in FIG. 2 shown first embodiment, a recess 60 is introduced into the housing cover 14a facing surface 11 of the housing body 10, which has an at least approximately flat bottom 61. The two high pressure bores 52 and 54 in the housing body 10 open into the recess 60 at a distance from each other. The depression 60 is thus larger in its cross section than the sum of the diameters of the two high-pressure bores 52, 54. The mouth of the high pressure bores 52,54 at the bottom 61 of the Recess 60 is preferably rounded in each case, which in turn can be easily produced by means of a form drill which can be attached to the flat bottom 61 of the depression 60. In the recess 60, a high-pressure bores 52,54 surrounding sealing ring 62 is inserted. A bore 50, which is arranged at least approximately centrally relative to the depression 60, which leads to the common high-pressure connection 42, is introduced into the housing cover 14a. The bore 50 extends at least approximately radially to the axis of rotation 19 of the drive shaft 18. The recess 60 facing the mouth of the bore 50 may be widened in diameter, for example, conical or rounded. The transition from the high-pressure bores 52, 54 in the housing body 10 to the bore 50 in the housing cover 14 a is sealed by the sealing ring 62. The bore 50 in the housing cover 14a and the outlet of the outlet cover 40 arranged in the housing cover 14a lead to the common high pressure port 42. The high pressure bores 52,54 extend in the housing body 10 without intersections and are merged in the recess 60 in the region of the transition from the housing body 10 to the housing cover 14a , The stress on the housing body 10 is thus kept so low that it can be made of inexpensive metal with sufficient strength and without special hardening treatment such as steel or at lower pressure generated by the pump elements 16 and light metal such as aluminum. Alternatively, when using a metal having high strength, as required in a course of the high-pressure bores with intersections, the pressure generated by the high-pressure pump can be increased while still ensuring a sufficient durability of the housing body 10. The housing cover 14 a, b, c have intersections, at the transition of the flow of the respective exhaust valve 40 into the bore 50 and are made of metal with a correspondingly higher strength than the housing body 10 made, for example, hardened steel.

In Figur 3 ist die Hochdruckpumpe gemäss einem zweiten Ausführungsbeispiel dargestellt, bei dem der Aufbau im wesentlichen gleich ist wie beim ersten Ausführungsbeispiel und zu dem nachfolgend nur die abweichenden Merkmale erläutert werden. In der dem Gehäusedeckel 14a zugewandten Fläche 11 des Gehäusekörpers 10 sind dabei zwei getrennte Vertiefungen 160 eingebracht, wobei in jede Vertiefung 160 eine Hochdruckbohrung 52 bzw. 54 mündet. Die Vertiefungen 160 weisen jeweils einen zumindest annähernd ebenen Boden 161 auf, und die Mündung der Hochdruckbohrung 52 bzw. 54 in der jeweiligen Vertiefung 160 ist vorzugsweise gerundet. Im Gehäusedeckel 14a sind entsprechend zwei Bohrungen 152,154 eingebracht, die die Hochdruckbohrungen 52,54 zum gemeinsamen Hochdruckanschluss 42 hin fortsetzen. In jede Vertiefung 160 ist ein die jeweilige Hochdruckbohrung 52 bzw. 54 umgebender Dichtring 162 eingesetzt, um den Übergang vom Gehäusekörper 10 zum Gehäusedeckel 14a abzudichten. Auch beim zweiten Ausführungsbeispiel verlaufen somit die Hochdruckbohrungen 52,54 im Gehäusekörper 10 ohne Verschneidungen und es sind nur im Gehäusedeckel 14a Verschneidungen vorhanden.In FIG. 3 is the high-pressure pump according to a second embodiment shown, in which the structure is substantially the same as in the first embodiment and to which only the deviating features are explained below. In the housing cover 14a facing surface 11 of the housing body 10 while two separate recesses 160 are introduced, wherein in each recess 160, a high-pressure bore 52 and 54 opens. The recesses 160 each have an at least approximately flat bottom 161, and the mouth of the high-pressure bore 52 or 54 in the respective recess 160 is preferably rounded. In the housing cover 14a correspondingly two bores 152,154 are introduced, which continue the high-pressure bores 52,54 to the common high pressure port 42 back. In each recess 160 is a respective high-pressure bore 52 and 54 surrounding sealing ring 162 is used to seal the transition from the housing body 10 to the housing cover 14a. Also in the second embodiment thus run the high pressure bores 52,54 in the housing body 10 without intersections and there are only in the housing cover 14a intersections.

Claims (8)

  1. High-pressure pump, in particular for a fuel injection device of an internal combustion engine, with a pump casing (10, 12, 14) in which a plurality of pump elements (16) are arranged, liquid being conveyed under high pressure by the pump elements (16) to a common high-pressure connection (42) via a high-pressure duct system, the pump casing having a casing body (10) and, for each pump element (16), a casing cover (14) covering the latter and connected to the casing body (10), characterized in that the high-pressure duct system has high-pressure bores (52, 54) which run, free of intersection, in the casing body (10) and which are united in the region of the transition from the casing body (10) to one of the casing covers (14a) or, in one of the casing covers (14a), to the common high-pressure connection (42).
  2. High-pressure pump according to Claim 1, characterized in that the common high-pressure connection (42) is arranged on the casing cover (14a).
  3. High-pressure pump according to Claim 1 or 2, characterized in that the high-pressure bores (52, 54) are united in the region of the transition from the casing body (10) to the casing cover (14a) and issue into a depression (60) which is introduced in the surface (11), facing the casing cover (14a), of the casing body (10) and from which a single bore (50) leads further on in the casing cover (14a) to the common high-pressure connection (42).
  4. High-pressure pump according to Claim 3, characterized in that the bottom (61) of the depression (60) is of at least approximately planar design, and in that the issues of the high-pressure bores (52, 54) on the bottom (61) of the depression (60) are rounded.
  5. High-pressure pump according to Claim 1 or 2, characterized in that the high-pressure bores (52, 54) issue in each case into a depression (160) introduced into a surface (11), facing the casing cover (14a), of the casing body (10), in that separate continuations (152, 154) of the high-pressure bores (52, 54) run in the casing cover (14a) and are united in the casing cover (14a) towards the common high-pressure connection (42).
  6. High-pressure pump according to Claim 5, characterized in that the bottom (161) of the depressions (160) is of at least approximately planar design, and in that the issues of the high-pressure bores (52, 54) on the bottom (161) of the depressions (160) are in each case rounded.
  7. High-pressure pump according to one of Claims 3 to 6, characterized in that in each case a sealing element (62; 162) for sealing off the transition from the casing body (10) to the casing cover (14a) is inserted into the depression (60) or depressions (160).
  8. High-pressure pump according to one of the preceding claims, characterized in that the casing body (10) consists of a metal of lower strength than the casing covers (14).
EP03807731A 2002-10-09 2003-06-20 High pressure pump, especially for a fuel injection device in an internal combustion engine Expired - Lifetime EP1552145B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10247142 2002-10-09
DE10247142A DE10247142A1 (en) 2002-10-09 2002-10-09 High pressure pump for fuel injection device has pump housing with body and cap to cover each pump element
PCT/DE2003/002061 WO2004033905A1 (en) 2002-10-09 2003-06-20 High pressure pump, especially for a fuel injection device in an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1552145A1 EP1552145A1 (en) 2005-07-13
EP1552145B1 true EP1552145B1 (en) 2010-06-02

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EP03807731A Expired - Lifetime EP1552145B1 (en) 2002-10-09 2003-06-20 High pressure pump, especially for a fuel injection device in an internal combustion engine

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US (1) US7178509B2 (en)
EP (1) EP1552145B1 (en)
JP (1) JP4384043B2 (en)
CN (1) CN100406722C (en)
DE (2) DE10247142A1 (en)
WO (1) WO2004033905A1 (en)

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DE102013210036A1 (en) * 2013-05-29 2014-12-04 Robert Bosch Gmbh High pressure pump for a fuel injection system
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Publication number Publication date
CN1688810A (en) 2005-10-26
WO2004033905A1 (en) 2004-04-22
DE50312780D1 (en) 2010-07-15
JP4384043B2 (en) 2009-12-16
US7178509B2 (en) 2007-02-20
US20060008363A1 (en) 2006-01-12
JP2006502338A (en) 2006-01-19
EP1552145A1 (en) 2005-07-13
DE10247142A1 (en) 2004-04-22
CN100406722C (en) 2008-07-30

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