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EP2188525B1 - Pump, particularly high-pressure fuel pump - Google Patents

Pump, particularly high-pressure fuel pump Download PDF

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Publication number
EP2188525B1
EP2188525B1 EP08802955A EP08802955A EP2188525B1 EP 2188525 B1 EP2188525 B1 EP 2188525B1 EP 08802955 A EP08802955 A EP 08802955A EP 08802955 A EP08802955 A EP 08802955A EP 2188525 B1 EP2188525 B1 EP 2188525B1
Authority
EP
European Patent Office
Prior art keywords
pump
drive shaft
pump piston
coupling device
indirectly
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.)
Not-in-force
Application number
EP08802955A
Other languages
German (de)
French (fr)
Other versions
EP2188525A1 (en
Inventor
Friedrich Boecking
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 EP2188525A1 publication Critical patent/EP2188525A1/en
Application granted granted Critical
Publication of EP2188525B1 publication Critical patent/EP2188525B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the invention relates to a pump, in particular high-pressure fuel pump according to the preamble of claim 1.
  • Such a pump is through the DE 73 05 570 U known, which represents the closest prior art.
  • This pump has at least one pump piston, which is tightly guided in a cylinder bore of a housing part of the pump.
  • the pump also has a drive shaft, which is provided with a drive section in the form of a cam or eccentric, by means of which the at least one pump piston is driven at least indirectly in a lifting movement.
  • the at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft.
  • the spring element is designed as a bow spring, which is connected to the pump piston and which extends over the circumference of the drive shaft on the opposite side of the drive shaft and is fixed there.
  • the bow spring forms a coupling element which extends past the drive shaft.
  • a pump having at least one pump piston which is tightly guided in a cylinder bore of a housing part of the pump.
  • the pump also has a drive shaft, which is provided with a drive section in the form of a cam or eccentric, by means of which the at least one pump piston is driven at least indirectly in a lifting movement.
  • the at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft.
  • the spring element is also designed here as a bow spring, which is connected to the pump piston and which extends over the circumference of the drive shaft on the opposite side of the drive shaft and is fixed there. Again, a large space over the circumference of the drive shaft is thus required, resulting in a corresponding size of the pump.
  • the pump according to the invention with the features of claim 1 has the advantage that the coupling device is arranged to save space, whereby the size of the pump can be kept low.
  • the pump according to the invention with the features of claim 1 has the advantage that by the arrangement of the spring element on the pump piston opposite side of the drive shaft, the housing part in the cylinder bore surrounding area with large
  • Wall thickness can be formed so that little or no
  • Training according to claim 2 is a simple design and space-saving
  • FIG. 1 fragmentary a pump in a longitudinal section
  • FIG. 2 the pump according to a modified version in a cross section along line II-II in FIG. 1
  • FIG. 3 a modified version of the pump in cross-section II-II.
  • a pump is shown, in particular a high-pressure fuel pump for a fuel injection of a
  • the pump has a housing 10 which may be formed in several parts and in which in a housing part 12, a rotationally driven drive shaft 14 is rotatably disposed about a rotation axis 15.
  • the drive shaft 14 is in the housing part 12 via two in the direction of the axis of rotation 15 of the drive shaft In a region lying between the two bearing points, the drive shaft 14 has at least one drive section 16, which is a cam or an eccentric
  • the pump has at least one or more pump elements, each with a pump piston 20 which is driven by the drive portion 16 of the drive shaft 14 at least indirectly in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14.
  • the pump piston 20 is tightly guided in a cylinder bore 22 of a housing part 24 of the pump. With its end facing away from the drive shaft 14, the pump piston 20 in the cylinder bore 22 defines a pump working chamber 26.
  • the pump working chamber 26 has a connection with an inlet 34 leading from a feed pump 32 via an inlet check valve 30 opening into the latter, via which the pump working chamber 26 radially inward to the axis of rotation 15 of the drive shaft 14 directed suction stroke of the pump piston 20 is filled with fuel.
  • the pump working chamber 26 also has an outlet check valve 36 which opens out of this connection with a drain 38 which leads, for example, to a high-pressure fuel accumulator 40 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotational axis 15 of the drive shaft 14 the pump working space 26 is displaced.
  • the housing part 24 has a flange-like region 42, which rests on the housing part 12, and a protruding from the region 42 cylindrical projection 44 which extends into an at least approximately radially to the axis of rotation 15 of the drive shaft 14 extending opening 46 which is formed for example as a bore, protrudes in the housing part 12.
  • the cylinder bore 22 extends from the end face of the projection 44 through the projection 44 into the region 42, where the pump working chamber 26 is arranged.
  • the inlet valve 30 and the outlet valve 36 are arranged.
  • a larger diameter centering collar 43 is provided in relation to the projection 44, which enters the bore 46 with little play and ensures centering of the housing part 24 with respect to the housing part 12.
  • the roller tappet 48 comprises a sleeve-shaped tappet body 50 guided in the bore 46 of the housing part 24, a roller shoe 52 inserted in the tappet body 50 and a roller 54 rotatably mounted in a housing 53 in the roller shoe 52.
  • the roller 54 rolls on the double cam 16 and is slid in the receptacle 53.
  • the plunger body 50 may also be guided over its inner jacket on the projection 44 of the housing part 24.
  • the pump piston 20 has an enlarged diameter in relation to the area guided in the cylinder bore 22 in the region of the piston foot, via which the pump piston 20 is coupled to the roller tappet 48 in the direction of its longitudinal axis
  • the drive portion 16 of the drive shaft 14 is formed as an eccentric, wherein the pump piston 20 rests directly or via a plunger, such as a cup tappet 148, on the eccentric or on a rotatably mounted on the eccentric ring 150.
  • the ring 150 may have an at least approximately flat flattening 152 in the region of the abutment of the pump piston 20 or of the plunger 148.
  • the installation of the pump piston 20 via the roller tappet 48 on the drive section 16 of the drive shaft 14 during the suction stroke of the pump piston 20 is ensured by a spring element 56.
  • the spring element 56 is arranged on the pump piston 20 opposite side of the drive shaft 14 in the housing 10 of the pump via a coupling device 58 at least indirectly on the pump piston 20 at.
  • the coupling device 58 is connected to the plunger body 50 of the roller tappet 48 and the plunger 148 and thus indirectly via this with the pump piston 20.
  • the coupling device 58 has two carrier-shaped parts 60, wherein in each case a carrier 60 laterally adjacent to the drive section 16th the drive shaft 14 is arranged.
  • the carriers 60 are designed such that they are as shown in FIG FIG.
  • the carrier 60 as in the Figures 2 and 3 illustrated a central hub-like region 62 with a large width in the region of the drive shaft 14 and to these subsequent, of the drive shaft 14 radially extending arms 64 with a smaller width.
  • the arms 64 are arranged at least approximately diametrically opposite each other.
  • a slot 66 is respectively introduced, through which the drive shaft 14 passes.
  • the two carriers 60 of the coupling device 58 are preferably formed identically in order to keep the production costs low.
  • the arms 64 of the carriers 60 of the coupling device 58 which extend to the tappet body 50, are connected at their end regions to the tappet body 50 or the tappet 148, for example by means of screws, rivets, by a welded connection or in some other way.
  • the arms 64 of the carrier 60 of the coupling device 58 extend approximately up to the level of the foot of the pump piston 20 and terminate at a distance in front of the end face of the projection 44 of the housing part 24.
  • the on the pump piston 20 remote from the side of the drive shaft 14 arranged arms 64 of the carrier 60 of the coupling device 58 are connected to each other by means of a plate-shaped member 68 at their ends.
  • the spring element 56 is designed, for example, as a cylindrical helical compression spring and clamped between the component 68 and a housing 10 of the pump, the drive portion 16 of the drive shaft 14 arranged adjacent stationary support 70.
  • the stationary support 70 is arranged at a sufficient distance from the drive section 16 in order to avoid contact with the drive section 16 during the rotation of the drive shaft 14.
  • the pump piston 20 performs a lifting movement together with the roller tappet 48.
  • This lifting movement also carries out the coupling device 58, wherein the spring element 56 is alternately compressed and relaxed.
  • the coupling device 58 Through the elongated holes 66 in the carriers 60 of the coupling device 58, the lifting movement of the coupling device 58 with respect to the drive shaft 14 is made possible.
  • Due to the arrangement of the spring element 56 on the pump piston 20 opposite side of the drive shaft 14 is between the portion 44 of the housing part 24 and the bore 46 in the housing part 12 only an annular gap with a small width for receiving the plunger body 50 is required.
  • the plunger body 50 can be designed with a small wall thickness, so that the annular gap is correspondingly narrow can be held.
  • the pump may also have a plurality, for example two pump pistons 20.
  • the two pump pistons 20 can be arranged at an angle of about 90 ° about the axis of rotation 15 of the drive shaft 14 to each other rotated, in which case the associated spring element 56 acts on each pump piston 20 via a coupling device 58, which on the pump piston 20 opposite side of Drive shaft 14 is arranged.
  • the coupling devices 58 of the two pump pistons 20 preferably extend in the direction of the axis of rotation 15 of the drive shaft 14 to each other, so that they do not interfere with each other.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

The invention relates to a pump, particularly a high-pressure fuel pump, having a housing, a drive shaft that is rotationally driven and has at least one drive section, and at least one pump piston, which is guided in a cylinder bore of a housing part of the pump in a sealed manner and which is driven by the drive section of the drive shaft at least indirectly in a lifting motion. The at least one pump piston is acted on by a spring element at least indirectly toward the drive section of the drive shaft. The spring element is disposed on the side of the drive shaft opposite the pump piston, and via a coupling device extending past the drive shaft it engages at least indirectly on the pump piston.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Pumpe, insbesondere Kraftstoffhochdruckpumpe nach der Gattung des Anspruchs 1.The invention relates to a pump, in particular high-pressure fuel pump according to the preamble of claim 1.

Eine solche Pumpe ist durch die DE 73 05 570 U bekannt, die den nächstkommenden Stand der Technik darstellt Diese Pumpe weist wenigstens einen Pumpenkolben auf, der in einer Zylinderbohrung eines Gehäuseteils der Pumpe dicht geführt ist. Die Pumpe weist außerdem eine Antriebswelle auf, die mit einem Antriebsabschnitt in Form eines Nockens oder Exzenters versehen ist, durch den der wenigstens eine Pumpenkolben zumindest mittelbar in einer Hubbewegung angetrieben wird. Der wenigstens eine Pumpenkolben ist durch ein Federelement zumindest mittelbar zum Antriebsabschnitt der Antriebswelle hin beaufschlagt. Beim Förderhub des Pumpenkolbens wird dieser gegen die Kraft des Federelements durch den Antriebsabschnitt in die Zylinderbohrung hineinbewegt und beim Saughub des Pumpenkolbens wird dieser durch die Kraft des Federelements aus der Zylinderbohrung herausbewegt. Das Federelement ist als eine Bügelfeder ausgebildet, die mit dem Pumpenkolben verbunden ist und die über den Umfang der Antriebswelle auf die gegenüberliegende Seite der Antriebswelle verläuft und dort befestigt ist. Die Bügelfeder bildet dabei ein Kopplungselement, das an der Antriebswelle vorbei verläuft. Bei dieser Ausbildung und Anordnung des Federelements ist ein großer Bauraum über den Umfang der Antriebswelle erforderlich, was zu einer entsprechend großen Baugröße der Pumpe führt.Such a pump is through the DE 73 05 570 U known, which represents the closest prior art. This pump has at least one pump piston, which is tightly guided in a cylinder bore of a housing part of the pump. The pump also has a drive shaft, which is provided with a drive section in the form of a cam or eccentric, by means of which the at least one pump piston is driven at least indirectly in a lifting movement. The at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft. During the delivery stroke of the pump piston, it is moved against the force of the spring element by the drive section into the cylinder bore, and during the suction stroke of the pump piston it is moved out of the cylinder bore by the force of the spring element. The spring element is designed as a bow spring, which is connected to the pump piston and which extends over the circumference of the drive shaft on the opposite side of the drive shaft and is fixed there. The bow spring forms a coupling element which extends past the drive shaft. In this design and arrangement of the spring element, a large space over the circumference of the drive shaft is required, resulting in a correspondingly large size of the pump.

Durch die DE 195 03 621 A1 ist ebenfalls eine Pumpe bekannt, die wenigstens einen Pumpenkolben aufweist, der in einer Zylinderbohrung eines Gehäuseteils der Pumpe dicht geführt ist. Die Pumpe weist außerdem eine Antriebswelle auf, die mit einem Antriebsabschnitt in Form eines Nockens oder Exzenters versehen ist, durch den der wenigstens eine Pumpenkolben zumindest mittelbar in einer Hubbewegung angetrieben wird. Der wenigstens eine Pumpenkolben ist durch ein Federelement zumindest mittelbar zum Antriebsabschnitt der Antriebswelle hin beaufschlagt. Beim Förderhub des Pumpenkolbens wird dieser gegen die Kraft des Federelements durch den Antriebsabschnitt in die Zylinderbohrung hineinbewegt und beim Saughub des Pumpenkolbens wird dieser durch die Kraft des Federelements aus der Zylinderbohrung herausbewegt. Das Federelement ist hier ebenfalls als eine Bügelfeder ausgebildet, die mit dem Pumpenkolben verbunden ist und die über den Umfang der Antriebswelle auf die gegenüberliegende Seite der Antriebswelle verläuft und dort befestigt ist. Auch hier ist somit ein großer Bauraum über den Umfang der Antriebswelle erforderlich, was zu einer entsprechenden Baugröße der Pumpe führt.By the DE 195 03 621 A1 is also known a pump having at least one pump piston which is tightly guided in a cylinder bore of a housing part of the pump. The pump also has a drive shaft, which is provided with a drive section in the form of a cam or eccentric, by means of which the at least one pump piston is driven at least indirectly in a lifting movement. The at least one pump piston is acted upon by a spring element at least indirectly to the drive portion of the drive shaft. During the delivery stroke of the pump piston, it is moved against the force of the spring element by the drive section into the cylinder bore, and during the suction stroke of the pump piston it is moved out of the cylinder bore by the force of the spring element. The spring element is also designed here as a bow spring, which is connected to the pump piston and which extends over the circumference of the drive shaft on the opposite side of the drive shaft and is fixed there. Again, a large space over the circumference of the drive shaft is thus required, resulting in a corresponding size of the pump.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Pumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass die Kopplungsvorrichtung platzsparend angeordnet ist, wodurch die Baugröße der Pumpe gering gehalten werden kann.The pump according to the invention with the features of claim 1 has the advantage that the coupling device is arranged to save space, whereby the size of the pump can be kept low.

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

Die erfindungsgemäße Pumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass durch die Anordnung des Federelements auf der dem Pumpenkolben gegenüberliegenden Seite der Antriebswelle das Gehäuseteil in dessen die Zylinderbohrung umgebendem Bereich mit großerThe pump according to the invention with the features of claim 1 has the advantage that by the arrangement of the spring element on the pump piston opposite side of the drive shaft, the housing part in the cylinder bore surrounding area with large

Wandstärke ausgebildet werden kann, so dass keine oder nur geringeWall thickness can be formed so that little or no

Leckageverluste durch eine Aufweitung der Zylinderbohrung entstehen.Leakage losses caused by an expansion of the cylinder bore.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen undIn the dependent claims are advantageous embodiments and

Weiterbildungen der erfindungsgemäßen Pumpe angegeben. Durch dieFurther developments of the pump according to the invention indicated. By the

Ausbildung gemäß Anspruch 2 ist eine einfache Ausführung und platzsparendeTraining according to claim 2 is a simple design and space-saving

Anordnung der Kopplungsvorrichtung ermöglichtArrangement of the coupling device allows

Zeichnungendrawings

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ausschnittsweise eine Pumpe in einem Längsschnitt, Figur 2 die Pumpe gemäβ einer modifitierten Ausführung in einem Querschnitt entlang Linie II-II in Figur 1 und Figur 3 eine modifizierte Ausführung der Pumpe im Querschnitt II-II.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. Show it FIG. 1 fragmentary a pump in a longitudinal section, FIG. 2 the pump according to a modified version in a cross section along line II-II in FIG. 1 and FIG. 3 a modified version of the pump in cross-section II-II.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In den Figuren 1 bis 3 ist eine Pumpe dargestellt, die insbesondere eine Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einerIn the FIGS. 1 to 3 a pump is shown, in particular a high-pressure fuel pump for a fuel injection of a

Brennkraftmaschine ist Die Pumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet sein kann und in dem in einem Gehäuseteil 12 eine rotierend angetriebene Antriebswelle 14 um eine Drehachse 15 drehbar angeordnet ist Die Antriebswelle 14 ist im Gehäuseteil 12 über zwei in Richtung der Drehachse 15 der Antriebswelle 14 voneinander beabstandete Lagerstellen gelagert In einem zwischen den beiden Lagerstellen liegenden Bereich weist die Antriebswelle 14 wenigstens einen Antriebsabschnitt 16 auf, der ein Nocken oder ein ExzenterInternal combustion engine is The pump has a housing 10 which may be formed in several parts and in which in a housing part 12, a rotationally driven drive shaft 14 is rotatably disposed about a rotation axis 15. The drive shaft 14 is in the housing part 12 via two in the direction of the axis of rotation 15 of the drive shaft In a region lying between the two bearing points, the drive shaft 14 has at least one drive section 16, which is a cam or an eccentric

sein kann. Die Pumpe weist wenigstens ein oder mehrere Pumpenelemente mit jeweils einem Pumpenkolben 20 auf, der durch den Antriebsabschnitt 16 der Antriebswelle 14 zumindest mittelbar in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 15 der Antriebswelle 14 angetrieben wird. Der Pumpenkolben 20 ist in einer Zylinderbohrung 22 eines Gehäuseteils 24 der Pumpe dicht geführt. Mit seinem der Antriebswelle 14 abgewandten Ende begrenzt der Pumpenkolben 20 in der Zylinderbohrung 22 einen Pumpenarbeitsraum 26. Der Pumpenarbeitsraum 26 weist über ein in diesen hinein öffnendes Einlassrückschlagvenfil 30 eine Verbindung mit einem von einer Förderpumpe 32 herführenden Zulauf 34 auf, über den der Pumpenarbeitsraum 26 beim radial nach innen zur Drehachse 15 der Antriebswelle 14 gerichteten Saughub des Pumpenkolbens 20 mit Kraftstoff befüllt wird. Der Pumpenarbeitsraum 26 weist außerdem über ein aus diesem heraus öffnendes Auslassrückschlagventil 36 eine Verbindung mit einem Ablauf 38 auf, der beispielsweise zu einem Kraftstoffhochdruckspeicher 40 führt und über den beim radial nach außen von der Drehachse 15 der Antriebswelle 14 weg gerichteten Förderhub des Pumpenkolbens 20 Kraftstoff aus dem Pumpenarbeitsraum 26 verdrängt wird.can be. The pump has at least one or more pump elements, each with a pump piston 20 which is driven by the drive portion 16 of the drive shaft 14 at least indirectly in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14. The pump piston 20 is tightly guided in a cylinder bore 22 of a housing part 24 of the pump. With its end facing away from the drive shaft 14, the pump piston 20 in the cylinder bore 22 defines a pump working chamber 26. The pump working chamber 26 has a connection with an inlet 34 leading from a feed pump 32 via an inlet check valve 30 opening into the latter, via which the pump working chamber 26 radially inward to the axis of rotation 15 of the drive shaft 14 directed suction stroke of the pump piston 20 is filled with fuel. The pump working chamber 26 also has an outlet check valve 36 which opens out of this connection with a drain 38 which leads, for example, to a high-pressure fuel accumulator 40 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotational axis 15 of the drive shaft 14 the pump working space 26 is displaced.

Das Gehäuseteil 24 weist einen flanschartigen Bereich 42 auf, der am Gehäuseteil 12 aufliegt, und einen vom Bereich 42 abstehenden zylindrischen Ansatz 44 auf, der in eine zumindest annähernd radial zur Drehachse 15 der Antriebswelle 14 verlaufende Öffnung 46, die beispielsweise als Bohrung ausgebildet ist, im Gehäuseteil 12 hineinragt. Die Zylinderbohrung 22 verläuft ausgehend von der Stirnseite des Ansatzes 44 durch den Ansatz 44 bis in den Bereich 42, wo der Pumpenarbeitsraum 26 angeordnet ist. Im Bereich 42 sind auch das Einlassventil 30 und das Auslassventil 36 angeordnet. Am Übergang vom Bereich 42 zum Ansatz 44 ist ein im Durchmesser gegenüber dem Ansatz 44 größerer Zentrierbund 43 vorgesehen, der mit geringem Spiel in die Bohrung 46 eintritt und eine Zentrierung des Gehäuseteils 24 bezüglich des Gehäuseteils 12 sicherstellt.The housing part 24 has a flange-like region 42, which rests on the housing part 12, and a protruding from the region 42 cylindrical projection 44 which extends into an at least approximately radially to the axis of rotation 15 of the drive shaft 14 extending opening 46 which is formed for example as a bore, protrudes in the housing part 12. The cylinder bore 22 extends from the end face of the projection 44 through the projection 44 into the region 42, where the pump working chamber 26 is arranged. In the area 42, the inlet valve 30 and the outlet valve 36 are arranged. At the transition from region 42 to the projection 44, a larger diameter centering collar 43 is provided in relation to the projection 44, which enters the bore 46 with little play and ensures centering of the housing part 24 with respect to the housing part 12.

Beim dargestellten Ausführungsbeispiel ist der Antriebsabschnitt 16 der Antriebswelle 14 gemäß Figur 2 als Doppelnocken ausgebildet und der Pumpenkolben 20 stützt sich über einen Rollenstößel 48 am Doppelnocken ab. Der Rollenstößel 48 umfasst einen in der Bohrung 46 des Gehäuseteils 24 über seinen Außenmantel geführten hülsenförmigen Stößelkörper 50, einen im Stößelkörper 50 eingesetzten Rollenschuh 52 und eine in einer Aufnahme 53 im Rollenschuh 52 drehbar gelagerte Rolle 54. Die Rolle 54 rollt auf dem Doppelnocken 16 ab und ist in der Aufnahme 53 gleitend geführt. Alternativ kann der Stößelkörper 50 auch über seinen Innenmantel auf dem Ansatz 44 des Gehäuseteils 24 geführt sein. Der Pumpenkolben 20 weist einen im Durchmesser gegenüber dem in der Zylinderbohrung 22 geführten Bereich vergrößerten Kolbenfuß auf, über den der Pumpenkolben 20 mit dem Rollenstößel 48 in Richtung seiner Längsachse gekoppelt istIn the illustrated embodiment, the drive portion 16 of the drive shaft 14 according to FIG. 2 designed as a double cam and the pump piston 20 is supported via a roller tappet 48 on the double cam. The roller tappet 48 comprises a sleeve-shaped tappet body 50 guided in the bore 46 of the housing part 24, a roller shoe 52 inserted in the tappet body 50 and a roller 54 rotatably mounted in a housing 53 in the roller shoe 52. The roller 54 rolls on the double cam 16 and is slid in the receptacle 53. Alternatively, the plunger body 50 may also be guided over its inner jacket on the projection 44 of the housing part 24. The pump piston 20 has an enlarged diameter in relation to the area guided in the cylinder bore 22 in the region of the piston foot, via which the pump piston 20 is coupled to the roller tappet 48 in the direction of its longitudinal axis

Alternativ kann auch gemäß einer in Figur 3 dargestellten modifizierten Ausführung der Pumpe vorgesehen sein, dass der Antriebsabschnitt 16 der Antriebswelle 14 als Exzenter ausgebildet ist, wobei der Pumpenkolben 20 direkt oder über einen Stößel, beispielsweise einen Tassenstößel 148, am Exzenter oder an einem auf dem Exzenter drehbar gelagerten Ring 150 anliegt. Der Ring 150 kann im Bereich der Anlage des Pumpenkolbens 20 bzw. des Stößels 148 eine zumindest annähernd ebene Abflachung 152 aufweisen.Alternatively, according to an in FIG. 3 shown modified embodiment of the pump may be provided that the drive portion 16 of the drive shaft 14 is formed as an eccentric, wherein the pump piston 20 rests directly or via a plunger, such as a cup tappet 148, on the eccentric or on a rotatably mounted on the eccentric ring 150. The ring 150 may have an at least approximately flat flattening 152 in the region of the abutment of the pump piston 20 or of the plunger 148.

Die Anlage des Pumpenkolbens 20 über den Rollenstößel 48 am Antriebsabschnitt 16 der Antriebswelle 14 beim Saughub des Pumpenkolbens 20 wird durch ein Federelement 56 sichergestellt Das Federelement 56 ist auf der dem Pumpenkolben 20 gegenüberliegenden Seite der Antriebswelle 14 im Gehäuse 10 der Pumpe angeordnet Das Federelement 56 greift über eine Kopplungsvorrichtung 58 zumindest mittelbar am Pumpenkolben 20 an. Beim dargestellten Ausführungsbeispiel ist die Kopplungsvorrichtung 58 mit dem Stößelkörper 50 des Rollenstößels 48 bzw. dem Stößel 148 verbunden und über diesen somit mittelbar mit dem Pumpenkolben 20. Die Kopplungsvorrichtung 58 weist zwei trägerförmige Teile 60 auf, wobei jeweils ein Träger 60 seitlich neben dem Antriebsabschnitt 16 der Antriebswelle 14 angeordnet ist Die Träger 60 sind so ausgebildet, dass diese wie in Figur 1 dargestellt in Richtung der Drehachse 15 der Antriebswelle 14 eine geringe Dicke aufweisen. In Richtung der Drehachse 15 der Antriebswelle 15 betrachtet weisen die Träger 60 wie in den Figuren 2 und 3 dargestellt einen mittleren nabenartigen Bereich 62 mit großer Breite im Bereich der Antriebswelle 14 und an diesen anschließende, von der Antriebswelle 14 radial wegverlaufende Arme 64 mit geringerer Breite auf. Die Arme 64 sind einander zumindest annähernd diametral gegenüberliegende angeordnet. Im Nabenbereich 62 der Träger 60 ist jeweils ein Langloch 66 eingebracht, durch das die Antriebswelle 14 hindurchtritt. Die beiden Träger 60 der Kopplungsvorrichtung 58 sind vorzugsweise identisch ausgebildet, um den Fertigungsaufwand gering zu halten.The installation of the pump piston 20 via the roller tappet 48 on the drive section 16 of the drive shaft 14 during the suction stroke of the pump piston 20 is ensured by a spring element 56. The spring element 56 is arranged on the pump piston 20 opposite side of the drive shaft 14 in the housing 10 of the pump via a coupling device 58 at least indirectly on the pump piston 20 at. In the illustrated embodiment, the coupling device 58 is connected to the plunger body 50 of the roller tappet 48 and the plunger 148 and thus indirectly via this with the pump piston 20. The coupling device 58 has two carrier-shaped parts 60, wherein in each case a carrier 60 laterally adjacent to the drive section 16th the drive shaft 14 is arranged. The carriers 60 are designed such that they are as shown in FIG FIG. 1 shown in the direction of the axis of rotation 15 of the drive shaft 14 have a small thickness. Viewed in the direction of the axis of rotation 15 of the drive shaft 15, the carrier 60 as in the Figures 2 and 3 illustrated a central hub-like region 62 with a large width in the region of the drive shaft 14 and to these subsequent, of the drive shaft 14 radially extending arms 64 with a smaller width. The arms 64 are arranged at least approximately diametrically opposite each other. In the hub region 62 of the carrier 60, a slot 66 is respectively introduced, through which the drive shaft 14 passes. The two carriers 60 of the coupling device 58 are preferably formed identically in order to keep the production costs low.

Die zum Stößelkörper 50 verlaufenden Arme 64 der Träger 60 der Kopplungsvorrichtung 58 sind an ihren Endbereichen mit dem Stößelkörper 50 bzw. dem Stößel 148 verbunden, beispielsweise mittels Schrauben, Nieten, durch eine Schweißverbindung oder auf andere Weise. Die Arme 64 der Träger 60 der Kopplungsvorrichtung 58 erstrecken sich etwa bis auf Höhe des Fußes des Pumpenkolbens 20 und enden mit Abstand vor der Stirnseite des Ansatzes 44 des Gehäuseteils 24. Die auf der dem Pumpenkolben 20 abgewandten Seite der Antriebswelle 14 angeordneten Arme 64 der Träger 60 der Kopplungsvorrichtung 58 sind mittels eines tellerförmigen Bauteils 68 an ihren Enden miteinander verbunden. Das Federelement 56 ist beispielsweise als zylindrische Schraubendruckfeder ausgebildet und zwischen dem Bauteil 68 und einer im Gehäuse 10 der Pumpe dem Antriebsabschnitt 16 der Antriebswelle 14 benachbart angeordneten ortsfesten Abstützung 70 eingespannt. Die ortsfeste Abstützung 70 ist dabei mit ausreichend Abstand vom Antriebsabschnitt 16 angeordnet, um bei der Drehung der Antriebswelle 14 eine Berührung mit dem Antriebsabschnitt 16 zu vermeiden.The arms 64 of the carriers 60 of the coupling device 58, which extend to the tappet body 50, are connected at their end regions to the tappet body 50 or the tappet 148, for example by means of screws, rivets, by a welded connection or in some other way. The arms 64 of the carrier 60 of the coupling device 58 extend approximately up to the level of the foot of the pump piston 20 and terminate at a distance in front of the end face of the projection 44 of the housing part 24. The on the pump piston 20 remote from the side of the drive shaft 14 arranged arms 64 of the carrier 60 of the coupling device 58 are connected to each other by means of a plate-shaped member 68 at their ends. The spring element 56 is designed, for example, as a cylindrical helical compression spring and clamped between the component 68 and a housing 10 of the pump, the drive portion 16 of the drive shaft 14 arranged adjacent stationary support 70. The stationary support 70 is arranged at a sufficient distance from the drive section 16 in order to avoid contact with the drive section 16 during the rotation of the drive shaft 14.

Beim Betrieb der Pumpe führt der Pumpenkolben 20 zusammen mit dem Rollenstößel 48 eine Hubbewegung aus. Diese Hubbewegung führt auch die Kopplungsvorrichtung 58 aus, wobei das Federelement 56 abwechselnd komprimiert und entspannt wird. Durch die Langlöcher 66 in den Trägern 60 der Kopplungsvorrichtung 58 ist die Hubbewegung der Kopplungsvorrichtung 58 bezüglich der Antriebswelle 14 ermöglicht. Durch die Anordnung des Federelements 56 auf der dem Pumpenkolben 20 gegenüberliegenden Seite der Antriebswelle 14 ist zwischen dem Abschnitt 44 des Gehäuseteils 24 und der Bohrung 46 im Gehäuseteil 12 nur ein Ringspalt mit geringer Breite zur Aufnahme des Stößelkörpers 50 erforderlich. Der Stößelkörper 50 kann dabei mit geringer Wandstärke ausgeführt werden, so dass der Ringspalt entsprechend schmal gehalten werden kann. Dies ermöglicht eine Ausführung des Ansatzes 44 des Gehäuseteils 24 bis zu dessen Stirnseite mit großer Wandstärke, wodurch sich die Zylinderbohrung 22 unter der Wirkung des Hochdrucks im Pumpenarbeitsraum 26 beim Förderhub des Pumpenkolbens 20 nur wenig aufweitet und entsprechend geringe Leckageverluste aus dem Pumpenarbeitsraum 26 auftreten.During operation of the pump, the pump piston 20 performs a lifting movement together with the roller tappet 48. This lifting movement also carries out the coupling device 58, wherein the spring element 56 is alternately compressed and relaxed. Through the elongated holes 66 in the carriers 60 of the coupling device 58, the lifting movement of the coupling device 58 with respect to the drive shaft 14 is made possible. Due to the arrangement of the spring element 56 on the pump piston 20 opposite side of the drive shaft 14 is between the portion 44 of the housing part 24 and the bore 46 in the housing part 12 only an annular gap with a small width for receiving the plunger body 50 is required. The plunger body 50 can be designed with a small wall thickness, so that the annular gap is correspondingly narrow can be held. This allows an embodiment of the projection 44 of the housing part 24 up to its front side with a large wall thickness, whereby the cylinder bore 22 under the action of the high pressure in the pump working chamber 26 during delivery of the pump piston 20 only slightly expands and correspondingly low leakage losses from the pump working chamber 26 occur.

Bei der vorstehenden Beschreibung ist nur ein Pumpenkolben 20 erläutert, wobei die Pumpe auch mehrere, beispielsweise zwei Pumpenkolben 20 aufweisen kann. Die beiden Pumpenkolben 20 können dabei unter einem Winkel von etwa 90° um die Drehachse 15 der Antriebswelle 14 zueinander verdreht angeordnet sein, wobei dann an jedem Pumpenkolben 20 über eine Kopplungsvorrichtung 58 das zugeordnete Federelement 56 angreift, das auf der dem Pumpenkolben 20 gegenüberliegenden Seite der Antriebswelle 14 angeordnet ist. Die Kopplungsvorrichtungen 58 der beiden Pumpenkolben 20 verlaufen dabei vorzugsweise in Richtung der Drehachse 15 der Antriebswelle 14 zu einander versetzt, so dass diese sich gegenseitig nicht behindern.In the above description, only one pump piston 20 is explained, wherein the pump may also have a plurality, for example two pump pistons 20. The two pump pistons 20 can be arranged at an angle of about 90 ° about the axis of rotation 15 of the drive shaft 14 to each other rotated, in which case the associated spring element 56 acts on each pump piston 20 via a coupling device 58, which on the pump piston 20 opposite side of Drive shaft 14 is arranged. The coupling devices 58 of the two pump pistons 20 preferably extend in the direction of the axis of rotation 15 of the drive shaft 14 to each other, so that they do not interfere with each other.

Claims (6)

  1. Pump, in particular high-pressure fuel pump, with a casing (10, 12, 24), with a drive shaft (14) which is driven in rotation and has at least one drive portion (16), and with at least one pump piston (20) which is sealingly guided in a cylinder bore (22) of a casing part (24) of the pump and is driven at least indirectly in a lifting movement by the drive portion (16) of the drive shaft (14), the at least one pump piston (20) being acted upon at least indirectly by a spring element (56) towards the drive portion (16) of the drive shaft (14), the spring element (56) being arranged on that side of the drive shaft (14) which lies opposite the pump piston (20) and engaging at least indirectly on the pump piston (20) via a coupling device (58) running past the drive shaft (14), characterized in that the coupling device (58) has two bearers (60), in each case a bearer (60) being arranged laterally next to the drive portion (16) of the drive shaft (14) and being connected at least indirectly to the pump piston (20).
  2. Pump according to Claim 1, characterized in that the two bearers (60) of the coupling device (58) have in each case a long hole (66) through which the drive shaft (14) passes.
  3. Pump according to Claim 2, characterized in that, as seen in the direction of the axis of rotation (15) of the drive shaft (14), the bearers (60) of the coupling device (58) have in each case a middle region (62) of large width, in which the long hole (66) is arranged, and have in each case two arms (64) of smaller width emanating from the middle region (62) in a line opposite one another.
  4. Pump according to Claim 3, characterized in that the arms (64), facing the pump piston (20), of the bearers (60) of the coupling device (58) are connected at their end regions at least indirectly to the pump piston (20).
  5. Pump according to Claim 3 or 4, characterized in that the spring element (56) is tension-mounted between the end regions of the arms (64) of the coupling device (58) which face away from the pump piston (20) and a fixed support (70) arranged near the drive shaft (14).
  6. Pump according to one of the preceding claims, characterized in that the pump piston (20) bears via a supporting element (48) against the drive portion (16) of the drive shaft (14), and in that the coupling device (58) is connected to the supporting element (48).
EP08802955A 2007-08-16 2008-08-01 Pump, particularly high-pressure fuel pump Not-in-force EP2188525B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007038525A DE102007038525A1 (en) 2007-08-16 2007-08-16 Pump, in particular high-pressure fuel pump
PCT/EP2008/060172 WO2009021865A1 (en) 2007-08-16 2008-08-01 Pump, particularly high-pressure fuel pump

Publications (2)

Publication Number Publication Date
EP2188525A1 EP2188525A1 (en) 2010-05-26
EP2188525B1 true EP2188525B1 (en) 2011-07-20

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ID=40010491

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Application Number Title Priority Date Filing Date
EP08802955A Not-in-force EP2188525B1 (en) 2007-08-16 2008-08-01 Pump, particularly high-pressure fuel pump

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US (1) US8337178B2 (en)
EP (1) EP2188525B1 (en)
JP (1) JP5119332B2 (en)
KR (1) KR20100042646A (en)
CN (1) CN101779038B (en)
AT (1) ATE517257T1 (en)
DE (1) DE102007038525A1 (en)
WO (1) WO2009021865A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008000824A1 (en) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump
DE102010041340A1 (en) * 2010-09-24 2012-03-29 Robert Bosch Gmbh dowel pin
CN101985920B (en) * 2010-10-27 2012-07-04 牛彦波 Annular super-high pressure booster for water cutting machine or water cleaning machine
JP2013130114A (en) * 2011-12-21 2013-07-04 Bosch Corp Fuel supply pump
JP5677329B2 (en) * 2012-01-20 2015-02-25 日立オートモティブシステムズ株式会社 High pressure fuel supply pump with electromagnetically driven suction valve
DE102014220878A1 (en) * 2014-10-15 2016-04-21 Continental Automotive Gmbh High-pressure fuel pump

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Publication number Priority date Publication date Assignee Title
US1893216A (en) * 1928-03-15 1933-01-03 Abraham M Babitch Linkage for fuel pumps
US1893217A (en) * 1928-09-10 1933-01-03 Abraham M Babitch Fuel pump with lost motion lever
US2036452A (en) * 1934-12-06 1936-04-07 Gen Motors Corp Fuel pump
US2139347A (en) * 1936-04-08 1938-12-06 Gen Motors Corp Fuel pump
US2359960A (en) * 1943-08-12 1944-10-10 Chicago & Southern Air Lines I Pumping mechanism
US3314365A (en) * 1964-08-24 1967-04-18 Douglas E Ritchie Direct acting variable pump
DE7305570U (en) * 1973-02-14 1973-08-16 Zahnradfabrik Friedrichshafen Ag Resilient mounting of the piston in a radial piston machine
US3924970A (en) * 1973-11-28 1975-12-09 Gen Motors Corp Electrically controlled fuel pump
DE4027794C2 (en) * 1990-09-01 2002-06-20 Continental Teves Ag & Co Ohg Hydraulic radial piston pump
DE19503621A1 (en) * 1995-02-03 1996-08-08 Bosch Gmbh Robert Reciprocating pump
DE19848040A1 (en) * 1998-10-17 2000-04-20 Bosch Gmbh Robert Radial piston pump for high fuel pressure in IC engines with common-rail injection systems has two plates engaging fully on each other, and second back pressure valve between first plate and pump housing
US6506033B2 (en) * 2000-10-26 2003-01-14 Okenseiko Co., Ltd. Miniature pump with ball-plate drive
JP4439723B2 (en) * 2000-12-28 2010-03-24 株式会社ミクニ Fuel pump
DE102008000824A1 (en) * 2008-03-26 2009-10-01 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump

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Publication number Publication date
CN101779038A (en) 2010-07-14
ATE517257T1 (en) 2011-08-15
US8337178B2 (en) 2012-12-25
EP2188525A1 (en) 2010-05-26
DE102007038525A1 (en) 2009-02-19
US20110200463A1 (en) 2011-08-18
CN101779038B (en) 2012-11-14
JP5119332B2 (en) 2013-01-16
JP2010537096A (en) 2010-12-02
KR20100042646A (en) 2010-04-26
WO2009021865A1 (en) 2009-02-19

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