EP2635797B1 - Pump, in particular high-pressure fuel pump - Google Patents

Pump, in particular high-pressure fuel pump Download PDF

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Publication number
EP2635797B1
EP2635797B1 EP11770768.7A EP11770768A EP2635797B1 EP 2635797 B1 EP2635797 B1 EP 2635797B1 EP 11770768 A EP11770768 A EP 11770768A EP 2635797 B1 EP2635797 B1 EP 2635797B1
Authority
EP
European Patent Office
Prior art keywords
pump
drive shaft
support element
roller
pump piston
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
EP11770768.7A
Other languages
German (de)
French (fr)
Other versions
EP2635797A1 (en
Inventor
Matthias Greiner
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 EP2635797A1 publication Critical patent/EP2635797A1/en
Application granted granted Critical
Publication of EP2635797B1 publication Critical patent/EP2635797B1/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
    • 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
    • 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
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F04B1/043—Hydraulic arrangements
    • 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 WO 2005/088125 A1 known.
  • This pump has a pump element which has a guided in a cylinder bore of a housing part pump piston which is driven indirectly by a drive shaft in a lifting movement.
  • the pump piston is supported on the drive shaft via a support element and a roller rotatably mounted in the support element, at least approximately circular cylindrical.
  • the support element is guided at least indirectly in the direction of the stroke movement of the pump piston.
  • the support element and the pump piston are acted upon by a spring to the drive shaft.
  • the spring is non-rotatably connected at its end facing the drive shaft about its longitudinal axis with the support member and connected at its end remote from the drive shaft to its longitudinal axis non-rotatably connected to a housing part.
  • the pump piston is firmly connected to the support element and the support element is guided only via the pump piston in the direction of the stroke movement of the pump piston.
  • the support member has on its side facing the drive shaft a concave depression in which the roller is rotatably mounted. In operation of the pump, the roller is held by the bias of the spring while in the support member, however, a mounting of the support member in the pump is difficult because the roller is not held in the support element, so that it can fall out during assembly of the support member in the pump ,
  • a ball piston for hydraulic machines in which a ball is rotatably mounted in a recess of a support member.
  • the ball is held in the recess by means of a holding element attached to the carrier element.
  • the retaining element has an internal thread with which it is screwed onto the carrier element surrounding the ball.
  • the ball When assembling the ball piston, the ball must be inserted before screwing the retaining element in the recess of the support element.
  • Such a design and attachment of the retaining element is only possible with a ball, but not in a circular cylindrical role, as a screwing of the retaining element on the support member in a circular cylindrical roller not possible, since a rotation of the retaining element with respect to the elongated roller is not possible.
  • the preparation of the carrier element and the retaining element is also complicated because of the thread.
  • the pump according to the invention with the features of claim 1 has the advantage that the roller is held in the support element, wherein the holding element is simple and easily attached to the support member.
  • a pump which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine.
  • the pump has a housing 10, which may be designed in several parts and in which a rotationally driven drive shaft 14 is rotatably mounted about an axis of rotation 15.
  • the drive shaft 14 has at least one cam 16, which may also be a multiple cam.
  • the pump has at least one or more pump elements 18, each having a pump piston 20 which is at least indirectly driven by the cam 16 of the drive shaft 14 in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14 and in the direction of the longitudinal axis 21 of the pump piston 20 becomes. It can also be provided that the pump does not have its own drive shaft 14 and the pump piston 20 of the pump element 18 is driven by a shaft of the internal combustion engine having a cam 16 or eccentric.
  • the pump piston 20 is tightly guided in a cylinder bore 22 of a housing part 24 of the pump.
  • the housing part 24 has a flange-like region 25 and a cylindrical projection 26 protruding therefrom towards the drive shaft 14, in which the cylinder bore 22 extends.
  • the pump piston 20 in the cylinder bore 22 defines a pump working chamber 28.
  • the pump working chamber 28 has an inlet check valve 30 opening into this connection with an inlet 32 leading, for example, from a feed pump, via which the pump working chamber 28 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 28 also has an outlet check valve 34 which opens out of this connection with a drain 36, which for example leads to a high-pressure fuel accumulator 38 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotation axis 15 of the drive shaft 14 the pump working space 28 is displaced.
  • the pump piston 20 is supported indirectly via a support element in the form of a roller shoe 42 on the cam 16 of the drive shaft 14.
  • the roller shoe 42 has on its side facing the drive shaft 14 a concave recess 44 in which an at least approximately circular cylindrical roller 46 is rotatably mounted, wherein the axis of rotation of the roller 46 is designated 48.
  • the roller 46 extends on the cam 16 of the drive shaft 14 from.
  • the housing 10 of the high-pressure fuel pump is filled with fuel and the fuel is lubricated between the roller 46 and the recess 44 of the roller shoe 42.
  • the roller shoe 42 and connected thereto pump piston 20 are by a prestressed spring in the form of a cylindrical helical compression spring 50 to Drive shaft 14 acted upon towards, so that the roller 46 is held in contact with the cam 16.
  • the helical compression spring 50 surrounds the projection 26 of the housing part 24 and the longitudinal axis is at least approximately identical to the longitudinal axis 21 of the pump piston 20. From the flange portion 25 of the housing part 24 is inwardly, the neck 26 coaxially surrounding a collar 52 protruding.
  • the collar 52 has as in FIG. 6 represented in its circumference one in the direction of the longitudinal axis 21 of the pump piston 20 extending groove 54.
  • the end of the spring 50 protrudes into the annulus formed between the boss 26 and the collar 52 and the end portion 56 of the last turn of the spring 50 is bent radially outward from the longitudinal axis 21 and projects into the groove 54.
  • the spring 50 is thus non-rotatably connected to the housing part 24 via the end region 56 of its last turn about the longitudinal axis 21.
  • the roller shoe 42 is approximately cylindrical in shape with a round cross section, wherein on the drive shaft 14 side facing the recess 44 is provided. On the side facing away from the drive shaft 14 of the roller shoe 42, an opening in the form of a bore 58 is provided into which projects from the cylinder bore 22 projecting end portion of the pump piston 20.
  • the pump piston 20 is fixedly connected to the roller shoe 42, in particular by the end portion of the pump piston 20 is pressed into the bore 58 of the roller shoe 42.
  • a reduced diameter relative to the roller shoe 42 collar 60 is formed, which projects into the drive shaft 14 facing the end of the spring 50.
  • the recess 44 in the roller shoe 42 is formed, for example, that this as in FIG. 3 represented the roller 46 on the circumference of an angle ⁇ of a maximum of 180 ° surrounds. Preferably, the recess 44 surrounds the roller 46 for less than 180 °, in particular about 140 °.
  • a holding element 66 is provided, which is arranged on the drive shaft 14 facing side of the roller shoe 42 and is secured to the roller shoe 42.
  • the roller shoe 42 has, on its side facing the drive shaft 14, a recess 68 which is circular in cross-section, for example.
  • the holding element 66 is disc-shaped with the recess 68 corresponding cross-section and inserted into the recess 68, in particular pressed into the recess 68.
  • the holding element 66 has as in the Figures 3 and 5 6 illustrates a slot-shaped opening 70, through which the roller 46 projects toward the drive shaft 14, wherein the width of the slot 70 in the radial direction with respect to the axis of rotation 48 of the roller 46 is smaller than the diameter of the roller 46, so that the roller 46 does not pass through the slot 70 can pass.
  • the holding member 66 comes in its final assembled end position at the bottom 69 of the recess 68 of the roller shoe 42 for conditioning without the holding member 66 presses against the roller 46.
  • the lateral edges 71 of the slot 70 may, as in FIG. 3 be shown bevelled, with the width of the slot 70 increases toward the roller 46 out.
  • the bevel of the edges 71 of the slot 70 sharp edges are avoided during start-up of the roller 46.
  • the lateral edges 71 of the slot 70 may also be rounded.
  • the length of the slot 70 in the direction of the axis of rotation 48 of the roller 46 is only slightly larger than the length of the roller 46.
  • the holding member 66 holds the roller 46 in the recess 44 of the roller shoe 42 and forms a support for the roller 46, on which Roller 46 can come to rest in the direction of its axis of rotation 48.
  • the holding element 66 is preferably made of a material with high wear resistance, for example hard metal or ceramic.
  • the pointing in the direction of its axis of rotation 48 axial ends 47 of the roller 46, with which they can start on the support member 66 may be formed convex rounded.
  • the support member 42 is guided only via the pump piston 20 in the direction of the lifting movement of the pump piston 20 and has no guide in a housing part. A sufficiently large distance is present between the support element 42 and the surrounding housing part, so that fuel can flow between the underside of the drive shaft 14 and the top side of the support element 42 facing away from the drive shaft 14.
  • the support member 42 and the support member 66 need therefore have no through openings, which allow a flow through the support member 42 and the support member 66 between the bottom and top. If necessary, the support member 42 and the retainer 66 may still be provided with apertures 74 to facilitate flow therethrough.

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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)
  • Details Of Reciprocating Pumps (AREA)

Description

Der Erfindung betrifft eine Pumpe, insbesondere Kraftstoffhochdruckpumpe, gemäß dem Oberbegriff 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 WO 2005/088125 A1 bekannt. Diese Pumpe weist ein Pumpenelement auf, das einen in einer Zylinderbohrung eines Gehäuseteils geführten Pumpenkolben aufweist, der durch eine Antriebswelle mittelbar in einer Hubbewegung angetrieben wird. Der Pumpenkolben stützt sich über ein Stützelement und eine im Stützelement drehbar gelagerte, zumindest annähernd kreiszylinderförmige Rolle an der Antriebswelle ab. Das Stützelement ist zumindest mittelbar in Richtung der Hubbewegung des Pumpenkolbens geführt. Das Stützelement und der Pumpenkolben sind durch eine Feder zur Antriebswelle hin beaufschlagt. Die Feder ist an ihrem der Antriebswelle zugewandten Ende um ihre Längsachse unverdrehbar mit dem Stützelement verbunden und an ihrem der Antriebswelle abgewandten Ende um ihre Längsachse unverdrehbar mit einem Gehäuseteil verbunden. Der Pumpenkolben ist fest mit dem Stützelement verbunden und das Stützelement ist nur über den Pumpenkolben in Richtung der Hubbewegung des Pumpenkolbens geführt. Das Stützelement weist auf seiner der Antriebswelle zugewandten Seite eine konkave Vertiefung auf, in der die Rolle drehbar gelagert ist. Im Betrieb der Pumpe wird die Rolle durch die Vorspannung der Feder zwar im Stützelement gehalten, jedoch ist eine Montage des Stützelements in der Pumpe schwierig, da die Rolle im Stützelement nicht gehalten ist, so dass diese bei der Montage des Stützelements in der Pumpe herausfallen kann.Such a pump is through the WO 2005/088125 A1 known. This pump has a pump element which has a guided in a cylinder bore of a housing part pump piston which is driven indirectly by a drive shaft in a lifting movement. The pump piston is supported on the drive shaft via a support element and a roller rotatably mounted in the support element, at least approximately circular cylindrical. The support element is guided at least indirectly in the direction of the stroke movement of the pump piston. The support element and the pump piston are acted upon by a spring to the drive shaft. The spring is non-rotatably connected at its end facing the drive shaft about its longitudinal axis with the support member and connected at its end remote from the drive shaft to its longitudinal axis non-rotatably connected to a housing part. The pump piston is firmly connected to the support element and the support element is guided only via the pump piston in the direction of the stroke movement of the pump piston. The support member has on its side facing the drive shaft a concave depression in which the roller is rotatably mounted. In operation of the pump, the roller is held by the bias of the spring while in the support member, however, a mounting of the support member in the pump is difficult because the roller is not held in the support element, so that it can fall out during assembly of the support member in the pump ,

Durch die WO 2009/098095 A1 ist eine Pumpe bekannt, die gleich ausgebildet ist wie die Pumpe gemäß dem Dokument WO 2005/088125 A1 , so dass diese dieselben Nachteile aufweist.By the WO 2009/098095 A1 is known a pump which is the same design as the pump according to the document WO 2005/088125 A1 so that it has the same disadvantages.

Durch die GB 2 064 700 A ist ein Kugelkolben für hydraulische Maschinen bekannt, bei dem in einer Vertiefung eines Trägerelements eine Kugel drehbar gelagert ist. Die Kugel ist mittels eines am Trägerelement befestigten Halteelements in der Vertiefung gehalten. Das Halteelement weist dabei ein Innengewinde auf, mit dem es auf das die Kugel umgebende Trägerelement aufgeschraubt ist. Beim Zusammenbau des Kugelkolbens muss die Kugel vor dem Aufschrauben des Halteelements in die Vertiefung des Trägerelements eingefügt werden. Eine solche Ausbildung und Befestigung des Halteelements ist nur bei einer Kugel möglich, nicht jedoch bei einer kreiszylinderförmigen Rolle, da ein Aufschrauben des Halteelements auf das Stützelement bei einer kreiszylinderförmigen Rolle nicht möglich, da ein Verdrehen des Halteelements bezüglich der langgestreckten Rolle nicht möglich ist. Die Herstellung des Trägerelements und des Halteelements ist außerdem wegen der Gewinde aufwendig.By the GB 2 064 700 A a ball piston for hydraulic machines is known in which a ball is rotatably mounted in a recess of a support member. The ball is held in the recess by means of a holding element attached to the carrier element. The retaining element has an internal thread with which it is screwed onto the carrier element surrounding the ball. When assembling the ball piston, the ball must be inserted before screwing the retaining element in the recess of the support element. Such a design and attachment of the retaining element is only possible with a ball, but not in a circular cylindrical role, as a screwing of the retaining element on the support member in a circular cylindrical roller not possible, since a rotation of the retaining element with respect to the elongated roller is not possible. The preparation of the carrier element and the retaining element is also complicated because of the thread.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Pumpe mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass die Rolle im Stützelement gehalten ist, wobei das Halteelement einfach ausgebildet und auf einfache Weise am Stützelement befestigt ist.The pump according to the invention with the features of claim 1 has the advantage that the roller is held in the support element, wherein the holding element is simple and easily attached to the support member.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Pumpe angegeben. Durch die Ausbildung gemäß Anspruch 2 ist eine einfache und sichere Verbindung des Pumpenkolbens mit dem Stützelement ermöglicht. Durch die Ausbildung gemäß Anspruch 3 ist sichergestellt, dass die Rolle in der Vertiefung des Stützelements nicht verkantet. Durch die Ausbildung gemäß Anspruch 4 ist eine Abstützung der Rolle in axialer Richtung auf einfache Weise erreicht, die mit der Weiterbildung gemäß Anspruch 5 eine hohe Verschleißfestigkeit aufweist. Durch die Ausbildung gemäß Anspruch 6 ist eine verdrehfeste Verbindung der Feder auf einfache Weise erreicht. Die Ausbildung gemäß Anspruch 7 ermöglicht eine kostengünstige Herstellung des Stützelements und des Halteelements.In the dependent claims advantageous refinements and developments of the pump according to the invention are given. Due to the design according to claim 2, a simple and secure connection of the pump piston with the support element is made possible. The embodiment according to claim 3 ensures that the roller is not tilted in the recess of the support element. Due to the construction according to claim 4, a support of the roller in the axial direction is achieved in a simple manner, which has a high wear resistance with the development according to claim 5. Due to the construction according to claim 6, a rotationally fixed connection of the spring is achieved in a simple manner. The embodiment of claim 7 allows a cost-effective production of the support member and the holding member.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Figur 1
eine Pumpe in einem Längsschnitt,
Figur 2
einen in Figur 1 mit II bezeichneten Ausschnitt der Pumpe in vergrößerter Darstellung,
Figur 3
die Pumpe ausschnittsweise in einem Querschnitt entlang Linie III-III in Figur 2,
Figur 4
die Pumpe ausschnittsweise in einer Ansicht in Pfeilrichtung IV in Figur 2,
Figur 5
die Pumpe ausschnittsweise in einem Schnitt entlang Linie V-V in Figur 2 und
Figur 6
die Pumpe ausschnittsweise in einer Ansicht in Pfeilrichtung VI in Figur 1.
An embodiment of the invention is illustrated in the drawing and explained in more detail in the following description. Show it:
FIG. 1
a pump in a longitudinal section,
FIG. 2
one in FIG. 1 with II designated section of the pump in an enlarged view,
FIG. 3
the pump in sections in a cross section along line III-III in FIG. 2 .
FIG. 4
the pump in sections in a view in the direction of arrow IV in FIG. 2 .
FIG. 5
the pump in sections in a section along line VV in FIG. 2 and
FIG. 6
the pump in sections in a view in the direction of arrow VI in FIG. 1 ,

Beschreibung des AusführungsbeispielsDescription of the embodiment

In den Figuren 1 bis 6 ist eine Pumpe dargestellt, die insbesondere eine Kraftstoffhochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine ist. Die Pumpe weist ein Gehäuse 10 auf, das mehrteilig ausgebildet sein kann und in dem eine rotierend angetriebene Antriebswelle 14 um eine Drehachse 15 drehbar gelagert ist. Die Antriebswelle 14 weist wenigstens einen Nocken 16 auf, der auch ein Mehrfachnocken sein kann. Die Pumpe weist wenigstens ein oder mehrere Pumpenelemente 18 mit jeweils einem Pumpenkolben 20 auf, der durch den Nocken 16 der Antriebswelle 14 zumindest mittelbar in einer Hubbewegung in zumindest annähernd radialer Richtung zur Drehachse 15 der Antriebswelle 14 und in Richtung der Längsachse 21 des Pumpenkolbens 20 angetrieben wird. Es kann auch vorgesehen sein, dass die Pumpe keine eigene Antriebswelle 14 aufweist und der Pumpenkolben 20 des Pumpenelements 18 durch eine Welle der Brennkraftmaschine angetrieben wird, die einen Nocken 16 oder Exzenter aufweist.In the FIGS. 1 to 6 a pump is shown, which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine. The pump has a housing 10, which may be designed in several parts and in which a rotationally driven drive shaft 14 is rotatably mounted about an axis of rotation 15. The drive shaft 14 has at least one cam 16, which may also be a multiple cam. The pump has at least one or more pump elements 18, each having a pump piston 20 which is at least indirectly driven by the cam 16 of the drive shaft 14 in a lifting movement in at least approximately radial direction to the axis of rotation 15 of the drive shaft 14 and in the direction of the longitudinal axis 21 of the pump piston 20 becomes. It can also be provided that the pump does not have its own drive shaft 14 and the pump piston 20 of the pump element 18 is driven by a shaft of the internal combustion engine having a cam 16 or eccentric.

Der Pumpenkolben 20 ist in einer Zylinderbohrung 22 eines Gehäuseteils 24 der Pumpe dicht geführt. Das Gehäuseteil 24 weist einen flanschartigen Bereich 25 und einen von diesem zur Antriebswelle 14 hin abstehenden zylindrischen Ansatz 26 auf, in dem die Zylinderbohrung 22 verläuft. Mit seinem der Antriebswelle 14 abgewandten Ende begrenzt der Pumpenkolben 20 in der Zylinderbohrung 22 einen Pumpenarbeitsraum 28. Der Pumpenarbeitsraum 28 weist über ein in diesen hinein öffnendes Einlassrückschlagventil 30 eine Verbindung mit einem beispielsweise von einer Förderpumpe herführenden Zulauf 32 auf, über den der Pumpenarbeitsraum 28 beim radial nach innen zur Drehachse 15 der Antriebswelle 14 gerichteten Saughub des Pumpenkolbens 20 mit Kraftstoff befüllt wird. Der Pumpenarbeitsraum 28 weist außerdem über ein aus diesem heraus öffnendes Auslassrückschlagventil 34 eine Verbindung mit einem Ablauf 36 auf, der beispielsweise zu einem Kraftstoffhochdruckspeicher 38 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 28 verdrängt wird.The pump piston 20 is tightly guided in a cylinder bore 22 of a housing part 24 of the pump. The housing part 24 has a flange-like region 25 and a cylindrical projection 26 protruding therefrom towards the drive shaft 14, in which the cylinder bore 22 extends. With its end facing away from the drive shaft 14, the pump piston 20 in the cylinder bore 22 defines a pump working chamber 28. The pump working chamber 28 has an inlet check valve 30 opening into this connection with an inlet 32 leading, for example, from a feed pump, via which the pump working chamber 28 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 28 also has an outlet check valve 34 which opens out of this connection with a drain 36, which for example leads to a high-pressure fuel accumulator 38 and fuel via the delivery stroke of the pump piston 20 directed radially outward from the rotation axis 15 of the drive shaft 14 the pump working space 28 is displaced.

Der Pumpenkolben 20 stützt sich mittelbar über ein Stützelement in Form eines Rollenschuhs 42 am Nocken 16 der Antriebswelle 14 ab. Der Rollenschuh 42 weist auf seiner der Antriebswelle 14 zugewandten Seite eine konkav gekrümmte Vertiefung 44 auf, in der eine zumindest annähernd kreiszylinderförmige Rolle 46 drehbar gelagert ist, wobei die Drehachse der Rolle 46 mit 48 bezeichnet ist. Die Rolle 46 läuft auf dem Nocken 16 der Antriebswelle 14 ab. Das Gehäuse 10 der Kraftstoffhochdruckpumpe ist mit Kraftstoff gefüllt und durch den Kraftstoff erfolgt eine Schmierung zwischen der Rolle 46 und der Vertiefung 44 des Rollenschuhs 42. Der Rollenschuh 42 und der mit diesem verbundene Pumpenkolben 20 werden durch eine vorgespannte Feder in Form einer zylindrischen Schraubendruckfeder 50 zur Antriebswelle 14 hin beaufschlagt, so dass die Rolle 46 in Anlage am Nocken 16 gehalten wird.The pump piston 20 is supported indirectly via a support element in the form of a roller shoe 42 on the cam 16 of the drive shaft 14. The roller shoe 42 has on its side facing the drive shaft 14 a concave recess 44 in which an at least approximately circular cylindrical roller 46 is rotatably mounted, wherein the axis of rotation of the roller 46 is designated 48. The roller 46 extends on the cam 16 of the drive shaft 14 from. The housing 10 of the high-pressure fuel pump is filled with fuel and the fuel is lubricated between the roller 46 and the recess 44 of the roller shoe 42. The roller shoe 42 and connected thereto pump piston 20 are by a prestressed spring in the form of a cylindrical helical compression spring 50 to Drive shaft 14 acted upon towards, so that the roller 46 is held in contact with the cam 16.

Die Schraubendruckfeder 50 umgibt den Ansatz 26 des Gehäuseteils 24 und deren Längsachse ist zumindest annähernd identisch mit der Längsachse 21 des Pumpenkolbens 20. Vom flanschartigen Bereich 25 des Gehäuseteils 24 steht nach innen, den Ansatz 26 koaxial umgebend ein Kragen 52 hervor. Der Kragen 52 weist wie in Figur 6 dargestellt in seinem Umfang eine in Richtung der Längsachse 21 des Pumpenkolbens 20 verlaufende Nut 54 auf. Das Ende der Feder 50 ragt in den zwischen dem Ansatz 26 und dem Kragen 52 gebildeten Ringraum hinein und der Endbereich 56 der letzten Windung der Feder 50 ist radial zur Längsachse 21 nach außen gebogen und ragt in die Nut 54 hinein. Die Feder 50 ist somit über den Endbereich 56 ihrer letzten Windung um die Längsachse 21 unverdrehbar mit dem Gehäuseteil 24 verbunden.The helical compression spring 50 surrounds the projection 26 of the housing part 24 and the longitudinal axis is at least approximately identical to the longitudinal axis 21 of the pump piston 20. From the flange portion 25 of the housing part 24 is inwardly, the neck 26 coaxially surrounding a collar 52 protruding. The collar 52 has as in FIG. 6 represented in its circumference one in the direction of the longitudinal axis 21 of the pump piston 20 extending groove 54. The end of the spring 50 protrudes into the annulus formed between the boss 26 and the collar 52 and the end portion 56 of the last turn of the spring 50 is bent radially outward from the longitudinal axis 21 and projects into the groove 54. The spring 50 is thus non-rotatably connected to the housing part 24 via the end region 56 of its last turn about the longitudinal axis 21.

Der Rollenschuh 42 ist etwa zylinderförmig ausgebildet mit rundem Querschnitt, wobei auf dessen der Antriebswelle 14 zugewandter Seite die Vertiefung 44 vorgesehen ist. Auf der der Antriebswelle 14 abgewandten Seite des Rollenschuhs 42 ist eine Öffnung in Form einer Bohrung 58 vorgesehen in die der aus der Zylinderbohrung 22 herausragende Endbereich des Pumpenkolbens 20 hineinragt. Der Pumpenkolben 20 ist mit dem Rollenschuh 42 fest verbunden, insbesondere indem der Endbereich des Pumpenkolbens 20 in die Bohrung 58 des Rollenschuhs 42 eingepresst ist. Auf der der Antriebswelle 14 abgewandten Seite des Rollenschuhs 42 ist ein im Durchmesser gegenüber dem Rollenschuh 42 reduzierter Bund 60 ausgebildet, der in das der Antriebswelle 14 zugewandte Ende der Feder 50 hineinragt. Am Umfang des Bunds 60 ist wie in den Figuren 2 und 4 dargestellt eine in Richtung der Längsachse 21 verlaufende Nut 62 ausgebildet und der Endbereich 64 der letzten Windung der Feder 50 ist radial zur Längsachse 21 nach innen gebogen und ragt in die Nut 62 hinein. Die Feder 50 ist somit über den Endbereich 64 ihrer letzten Windung um die Längsachse 21 unverdrehbar mit dem Rollenschuh 42 verbunden.The roller shoe 42 is approximately cylindrical in shape with a round cross section, wherein on the drive shaft 14 side facing the recess 44 is provided. On the side facing away from the drive shaft 14 of the roller shoe 42, an opening in the form of a bore 58 is provided into which projects from the cylinder bore 22 projecting end portion of the pump piston 20. The pump piston 20 is fixedly connected to the roller shoe 42, in particular by the end portion of the pump piston 20 is pressed into the bore 58 of the roller shoe 42. On the side facing away from the drive shaft 14 side of the roller shoe 42 a reduced diameter relative to the roller shoe 42 collar 60 is formed, which projects into the drive shaft 14 facing the end of the spring 50. At the periphery of the collar 60 is like in the Figures 2 and 4 illustrated extending in the direction of the longitudinal axis 21 groove 62 and the end portion 64 of the last turn of the spring 50 is bent radially inwardly of the longitudinal axis 21 and protrudes into the groove 62 into it. The spring 50 is thus non-rotatably connected to the roller shoe 42 about the end portion 64 of its last turn about the longitudinal axis 21.

Die Vertiefung 44 im Rollenschuh 42 ist beispielsweise so ausgebildet, dass diese wie in Figur 3 dargestellt die Rolle 46 auf deren Umfang über einen Winkel α von maximal 180° umgibt. Vorzugsweise umgibt die Vertiefung 44 die Rolle 46 über weniger als 180°, insbesondere über etwa 140°. Um die Rolle 46 im Rollenschuh 42 zu halten ist ein Halteelement 66 vorgesehen, das auf der der Antriebswelle 14 zugewandten Seite des Rollenschuhs 42 angeordnet ist und am Rollenschuh 42 befestigt ist. Der Rollenschuh 42 weist auf seiner der Antriebswelle 14 zugewandten Seite eine im Querschnitt beispielsweise kreisförmige Ausnehmung 68 auf. Das Halteelement 66 ist scheibenförmig mit der Ausnehmung 68 entsprechendem Querschnitt ausgebildet und in die Ausnehmung 68 eingefügt, insbesondere in die Ausnehmung 68 eingepresst.The recess 44 in the roller shoe 42 is formed, for example, that this as in FIG. 3 represented the roller 46 on the circumference of an angle α of a maximum of 180 ° surrounds. Preferably, the recess 44 surrounds the roller 46 for less than 180 °, in particular about 140 °. In order to hold the roller 46 in the roller shoe 42, a holding element 66 is provided, which is arranged on the drive shaft 14 facing side of the roller shoe 42 and is secured to the roller shoe 42. The roller shoe 42 has, on its side facing the drive shaft 14, a recess 68 which is circular in cross-section, for example. The holding element 66 is disc-shaped with the recess 68 corresponding cross-section and inserted into the recess 68, in particular pressed into the recess 68.

Das Halteelement 66 weist wie in den Figuren 3 und 5 dargestellt eine schlitzförmige Öffnung 70 auf, durch die die Rolle 46 zur Antriebswelle 14 hin hindurchragt, wobei die Breite des Schlitzes 70 in radialer Richtung bezüglich der Drehachse 48 der Rolle 46 kleiner ist als der Durchmesser der Rolle 46, so dass die Rolle 46 nicht durch den Schlitz 70 hindurchtreten kann. Das Halteelement 66 kommt in seiner fertig montierten Endposition am Boden 69 der Ausnehmung 68 des Rollenschuhs 42 zur Anlage ohne dass das Halteelement 66 gegen die Rolle 46 drückt. Die seitlichen Ränder 71 des Schlitzes 70 können wie in Figur 3 dargestellt angeschrägt sein, wobei sich die Breite des Schlitzes 70 zur Rolle 46 hin vergrößert. Durch die Anschrägung der Ränder 71 des Schlitzes 70 werden scharfe Kanten beim Anlauf der Rolle 46 vermieden. Alternativ können die seitlichen Ränder 71 des Schlitzes 70 auch gerundet ausgebildet sein.The holding element 66 has as in the Figures 3 and 5 6 illustrates a slot-shaped opening 70, through which the roller 46 projects toward the drive shaft 14, wherein the width of the slot 70 in the radial direction with respect to the axis of rotation 48 of the roller 46 is smaller than the diameter of the roller 46, so that the roller 46 does not pass through the slot 70 can pass. The holding member 66 comes in its final assembled end position at the bottom 69 of the recess 68 of the roller shoe 42 for conditioning without the holding member 66 presses against the roller 46. The lateral edges 71 of the slot 70 may, as in FIG. 3 be shown bevelled, with the width of the slot 70 increases toward the roller 46 out. The bevel of the edges 71 of the slot 70 sharp edges are avoided during start-up of the roller 46. Alternatively, the lateral edges 71 of the slot 70 may also be rounded.

Die Länge des Schlitzes 70 in Richtung der Drehachse 48 der Rolle 46 ist nur wenig größer als die Länge der Rolle 46. Das Halteelement 66 hält die Rolle 46 in der Vertiefung 44 des Rollenschuhs 42 und bildet eine Abstützung für die Rolle 46, an der die Rolle 46 in Richtung ihrer Drehachse 48 zur Anlage kommen kann. Das Halteelement 66 ist vorzugsweise aus einem Material mit hoher Verschleißfestigkeit hergestellt, beispielsweise Hartmetall oder Keramik. Die in Richtung ihrer Drehachse 48 weisenden axialen Enden 47 der Rolle 46, mit denen diese am Halteelement 66 anlaufen kann, können konvex gerundet ausgebildet sein.The length of the slot 70 in the direction of the axis of rotation 48 of the roller 46 is only slightly larger than the length of the roller 46. The holding member 66 holds the roller 46 in the recess 44 of the roller shoe 42 and forms a support for the roller 46, on which Roller 46 can come to rest in the direction of its axis of rotation 48. The holding element 66 is preferably made of a material with high wear resistance, for example hard metal or ceramic. The pointing in the direction of its axis of rotation 48 axial ends 47 of the roller 46, with which they can start on the support member 66 may be formed convex rounded.

Das Stützelement 42 ist nur über den Pumpenkolben 20 in Richtung der Hubbewegung des Pumpenkolbens 20 geführt und weist keine Führung in einem Gehäuseteil auf. Zwischen dem Stützelement 42 und dem dieses umgebenden Gehäuseteil ist dabei ein ausreichend großer Abstand vorhanden, so dass Kraftstoff zwischen der der Antriebswelle 14 zugewandten Unterseite und der der Antriebswelle 14 abgewandten Oberseite des Stützelements 42 strömen kann. Das Stützelement 42 und das Halteelement 66 brauchen daher keine durchgehenden Öffnungen aufzuweisen, die eine Durchströmung des Stützelements 42 und des Halteelements 66 zwischen deren Unter- und Oberseite ermöglichen. Falls erforderlich können zur Ermöglichung einer Durchströmung das Stützelement 42 und das Halteelement 66 dennoch mit Öffnungen 74 versehen sein.The support member 42 is guided only via the pump piston 20 in the direction of the lifting movement of the pump piston 20 and has no guide in a housing part. A sufficiently large distance is present between the support element 42 and the surrounding housing part, so that fuel can flow between the underside of the drive shaft 14 and the top side of the support element 42 facing away from the drive shaft 14. The support member 42 and the support member 66 need therefore have no through openings, which allow a flow through the support member 42 and the support member 66 between the bottom and top. If necessary, the support member 42 and the retainer 66 may still be provided with apertures 74 to facilitate flow therethrough.

Claims (7)

  1. Pump, in particular high-pressure fuel pump, having at least one pump element (18) which has a pump piston (20) guided in a cylinder bore (22) of a housing part (24), which pump piston is indirectly driven in reciprocating movement by a drive shaft (14), wherein the pump piston (20) is supported on the drive shaft (14) via a support element (42) and via an at least approximately circular cylindrical roller (46) which is rotatably mounted in the support element (42), wherein the support element (42) is at least indirectly guided in the direction of the reciprocating movement of the pump piston (20), wherein the support element (42) and the pump piston (20) are forced toward the drive shaft (14) by a spring (50), wherein the spring (50), at its end facing toward the drive shaft (14), is connected, non-rotatably about its longitudinal axis (21), to the support element (42), and said spring, at its end averted from the drive shaft (14), is connected, non-rotatably about its longitudinal axis (21), to a housing part (24), wherein the pump piston (20) is fixedly connected to the support element (42) and the support element (42) is guided in the direction of the reciprocating movement of the pump piston (20) only by way of the pump piston (20), wherein the support element (42) has, on its side facing toward the drive shaft (14), a concave depression (44) in which the roller (46) is rotatably mounted, characterized in that, a holding element (66) for the roller (46) is fastened to that side of the support element (42) which faces toward the drive shaft (14), by means of which holding element the roller (46) is held in the support element (42), in that the support element (42), on its side facing toward the drive shaft (14), has a recess (68) surrounding the depression (44), in which recess the holding element (66) is fastened, in particular by being pressed in, and in that the holding element (66) has a slot-shaped opening (70) through which the roller (46) projects in the direction of the drive shaft (14).
  2. Pump according to Claim 1, characterized in that the support element (42) has, on its side averted from the drive shaft (14), an opening (58) in which that end of the pump piston (20) which projects out of the cylinder bore (22) is held, in particular by being pressed in.
  3. Pump according to Claim 1 or 2, characterized in that the depression (44) encompasses the roller (46) on its circumference over an angle (α) of at most 180°, preferably less than 180°.
  4. Pump according to one of Claims 1 to 3, characterized in that the holding element (66) forms a support for the roller (46) in the direction of the axis of rotation (48) thereof.
  5. Pump according to one of Claims 1 to 4, characterized in that the holding element (66) is produced from a material with high wear resistance, in particular from hard metal.
  6. Pump according to one of the preceding claims, characterized in that the spring (50) is a helical compression spring, the winding ends (56, 64) of which run in a radial direction with respect to the longitudinal axis (21) of the spring (50) and engage into corresponding receptacles (54, 62) of the housing part (24) and of the support element (40).
  7. Pump according to one of the preceding claims, characterized in that the support element (42) and the holding element (66) have no continuous openings between those sides thereof which face toward the drive shaft (14) and those sides thereof which are averted from the drive shaft (14).
EP11770768.7A 2010-11-05 2011-10-17 Pump, in particular high-pressure fuel pump Not-in-force EP2635797B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010043512 DE102010043512A1 (en) 2010-11-05 2010-11-05 Pump, in particular high-pressure fuel pump
PCT/EP2011/068097 WO2012059315A1 (en) 2010-11-05 2011-10-17 Pump, in particular high-pressure fuel pump

Publications (2)

Publication Number Publication Date
EP2635797A1 EP2635797A1 (en) 2013-09-11
EP2635797B1 true EP2635797B1 (en) 2015-10-07

Family

ID=44925499

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11770768.7A Not-in-force EP2635797B1 (en) 2010-11-05 2011-10-17 Pump, in particular high-pressure fuel pump

Country Status (4)

Country Link
EP (1) EP2635797B1 (en)
CN (1) CN103201499B (en)
DE (1) DE102010043512A1 (en)
WO (1) WO2012059315A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2915994A1 (en) * 2014-03-06 2015-09-09 Continental Automotive GmbH Tappet arrangement and pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2064700A (en) * 1979-09-13 1981-06-17 Leco Hydraulics Ltd Ball piston
SI9600292A (en) * 1996-10-02 1998-04-30 Mag. Manfreda Jurij, Dipl.Ing. Piston assembly of a radial-piston hydraulic engine
CN2440949Y (en) * 2000-09-08 2001-08-01 无锡威孚集团有限公司 Oil jetting pump
CN2663678Y (en) * 2003-07-28 2004-12-15 上海东维燃油喷射有限公司 High power type oil spout pump assembly
DE102004011284A1 (en) * 2004-03-09 2005-09-29 Robert Bosch Gmbh High-pressure pump, in particular for a fuel injection device of an internal combustion engine
DE102008007342A1 (en) * 2008-02-04 2009-08-06 Robert Bosch Gmbh Shear force-free cams for common-rail high-pressure pumps
DE102008000699A1 (en) 2008-03-17 2009-09-24 Robert Bosch Gmbh Fuel high-pressure pump for fuel injection system of internal-combustion engine, has pump housing and pump element, which has piston, where piston is driven by cam, where cam is operated with roller

Also Published As

Publication number Publication date
WO2012059315A1 (en) 2012-05-10
CN103201499B (en) 2016-10-05
DE102010043512A1 (en) 2012-05-10
EP2635797A1 (en) 2013-09-11
CN103201499A (en) 2013-07-10

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