EP2558707B1 - High pressure pump - Google Patents

High pressure pump Download PDF

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Publication number
EP2558707B1
EP2558707B1 EP11709037.3A EP11709037A EP2558707B1 EP 2558707 B1 EP2558707 B1 EP 2558707B1 EP 11709037 A EP11709037 A EP 11709037A EP 2558707 B1 EP2558707 B1 EP 2558707B1
Authority
EP
European Patent Office
Prior art keywords
roller
decline
cam
pressure pump
running surface
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
EP11709037.3A
Other languages
German (de)
French (fr)
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EP2558707A1 (en
Inventor
Friedrich Boecking
Arnold Gente
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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Publication date
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Publication of EP2558707A1 publication Critical patent/EP2558707A1/en
Application granted granted Critical
Publication of EP2558707B1 publication Critical patent/EP2558707B1/en
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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
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • 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
    • 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
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

Definitions

  • the invention relates to a high-pressure pump, in particular a radial or linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.
  • a high-pressure pump for a fuel injection device of an internal combustion engine has a pump housing, in which a pump element is arranged, which comprises a driven by a drive shaft in a stroke pump piston.
  • the pump piston is slidably guided in a cylinder bore of a part of the pump housing and limited in this one pump working space.
  • the pump piston is supported indirectly via a hollow cylindrical plunger on the drive shaft, wherein the plunger is slidably guided in a bore of a portion of the pump housing in the direction of the longitudinal axis of the pump piston.
  • the longitudinal axis of the plunger is substantially identical to the longitudinal axis of the pump piston.
  • the drive shaft facing end portion is a support member used in which a roller is rotatably mounted, which rolls on the cam of the drive shaft.
  • the axis of rotation of the roller is at least approximately parallel to the axis of rotation of the drive shaft.
  • the support member has on its side facing the drive shaft a recess in which the roller is mounted.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that a running behavior of the roller on the tread of the cam improves, and that the Abschlappung the tread and the roller are designed so that in a centered basic position of the roller between an end portion of the roller and the tread is formed a gap. Specifically, the hydrodynamics between the roller and a roller shoe can be improved and at the same time an advantageous running behavior of the roller on the tread of the cam can be achieved.
  • the tread is convex in the region of the Abschlappung.
  • the Abschlappung of the tread is designed so that even in a decentered position of the roller between the end portion of the roller and the tread a gap is formed.
  • a constantly small gap can be ensured.
  • the Abschlappung on the camshaft the role can be centered on its path.
  • the roller In an occurring angular error between the roller and the cam of the drive shaft, the roller is guided by the bending of the roller caused by the pressing force from the pressure generation around the cam through the Abschlappung.
  • an oblique cam run-up of the roll is counteracted by the Abschlappung. Specifically, thus a side start of the role can be prevented or at least avoided.
  • the gap formed between the end section of the roller and the running surface in a decentered position of the roller, in which the roller is adjusted from the centered basic position in the direction of the Abschlappung the tread at least approximately the same size as in FIG the centered basic position.
  • the Abschlappung the tread is formed up to a front side of the cam.
  • the tread has a central tread, which is designed at least approximately cylinder jacket-shaped and that the Abschlappung adjacent to the middle tread.
  • a roller shoe is provided, in which the roller is mounted, and that the roller shoe allows a certain displaceability of the roller perpendicular to a running direction of the roller on the tread.
  • the role is preferably configured substantially as a cylindrical roller.
  • the cam has a further Abschlappung on its tread and that the Abschlappung and further Abschlappung are configured symmetrically with respect to a centered basic position of the role.
  • the Abschlappung and further Abschlappung are designed so that the roller is guided in a centered basic position. Due to the Abschlappept on the cam thus the role is centered on its path. An oblique cam run-up of the roller is thus counteracted. As a result, a lateral start of the roller is prevented or at least avoided on both sides.
  • Fig. 1 shows a high pressure pump 1 in a schematic, axial sectional view according to an embodiment of the invention.
  • the high pressure pump 1 can be configured in particular as a radial or inline piston pump.
  • the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the high pressure pump 1 is for a fuel injection system with a fuel rail, a so-called common rail that stores diesel fuel under high pressure.
  • the high-pressure pump 1 according to the invention is also suitable for other applications.
  • the high-pressure pump 1 has a multipart pump housing 2.
  • the pump housing 2 comprises a housing part 3 and a flange 4 connected to the housing part 3. Furthermore, a cylinder head 5 is provided, which is connected to the housing part 3.
  • a drive shaft 6 is arranged in the pump housing 2.
  • the drive shaft 6 includes a cam 7.
  • the cam 7 can also be configured as a multiple cam.
  • the cam 7 can also be designed as an eccentric portion of the drive shaft 6.
  • a bearing 8 is formed in the housing part 3.
  • a further bearing 9 is provided on the flange 4.
  • the drive shaft 6 is mounted on the bearings 8, 9.
  • the drive shaft 6 rotates about its axis of rotation 10.
  • the bearings 8, 9 are spaced from each other with respect to the axis of rotation 10 and arranged on different sides of the cam 7.
  • the high-pressure pump 1 has a pump assembly 15.
  • the high-pressure pump 1 may also have a plurality of pump assemblies.
  • the pump assembly 15 can be driven by means of the cam 7 of the drive shaft 6. If the high-pressure pump 1 has further pump assemblies, these may be driven by the cam 7 together with the pump assembly 15. It is also possible that at least one further cam is provided on the drive shaft 6, which serves according to the cam 7 for driving at least one pump assembly. Depending on the configuration, a radial or series piston pump can thereby be realized.
  • the housing part 3 of the pump housing 2 has a bore 16.
  • a projection 17 is formed, which projects into the bore 16 of the housing part 3.
  • the pump assembly 15 is provided in the region of the projection 17 and the bore 16.
  • the approach 17 has a cylinder bore 18 in which a pump piston 19 is guided.
  • the pump piston 19 limits a pump working chamber 20 in the cylinder bore 18.
  • Fuel can enter the pump working chamber 20 via an inlet valve 21.
  • an outlet valve 22 is provided, via which fuel can be conveyed out of the pump working chamber 20 into a connecting line 23.
  • the connecting line 23 leads, for example, to a common rail.
  • the cylinder bore 18 has an axis 24 which is at least approximately pointing to the axis of rotation 10 and oriented perpendicular to the axis of rotation 10.
  • the pump piston 19 is slidable along the axis 24, as illustrated by the double arrow 25.
  • the pump assembly 15 also has a hollow cylindrical plunger body 26 which is guided in the bore 16. An inserted into the plunger body 26 driving element 27 engages behind a collar 28 of the pump piston 19. Here, the driving element 27 is acted upon by a plunger spring 29 in the direction of the cam 7. During a movement of the plunger body 26 thus the pump piston 19 is taken.
  • a roller shoe 30 is also used.
  • the collar 28 of the pump piston 19 abuts against the roller shoe 30.
  • a roller 31 is mounted, which is designed as a roller 31.
  • the roller 31 is in this case at least substantially cylindrical. This results in an advantageous guidance of the roller 31 in the roller shoe 30.
  • the cam 7 has an end face 32, which faces the bearing point 9, and a further end face 33, which faces the bearing point 8.
  • the end faces 32, 33 are remote from each other.
  • the cam 7 has a running surface 34.
  • the roller 31 runs, for example, in a running direction 35 along the running surface 34.
  • the running surface 34 has a central tread 36 on which the running surface 34 is configured at least approximately in the form of a cylinder jacket.
  • a centered basic position of the roller 31 is given to the tread 34, in the Fig. 1 is shown.
  • the roller 31 rotates about its axis 37.
  • the configuration of the high-pressure pump 1 is below also with reference to the Fig. 2 described in further detail.
  • Fig. 2 shows the in Fig. 1 With II designated section of the high-pressure pump 1 of the embodiment, wherein the roller shoe 30, the roller 31 and parts of the cam 7 are shown.
  • the cam 7 has on its tread 34 a Abschlappung 40 and a further Abschlappung 41.
  • the Abschlappung 40 extends to the end face 32.
  • the further Abschlappung 41 extends to the other end face 33.
  • the Abschlappeptept 40, 41 adjoin on both sides of the central tread 36 of the tread 34 at. In this embodiment, therefore, the middle tread 36 extends together with the two Abschlappieux 40, 41 over the entire running surface 34 of the cam. 7
  • the Abschlappened 40, 41 are configured as convex Abschlappungen 40, 41. With respect to the at least approximately cylindrical roller 31 are formed by the Abschlappept 40, 41 small gaps 42, 43 between the roller 31 and the tread 34.
  • the gaps 42, 43 in this case relate to an end portion 44 and a further end portion 45 of the roller 31.
  • a center piece 46 of the roller 31, however, is applied to the middle tread 36 at.
  • an angle error can occur at an angle 47. If an angular error occurs, then results between the roller shoe 30 with the roller 31 and the cam 7 and the axis 24, a non-vanishing angle 47. For a reliable operation of the high-pressure pump 1, such a game may also be required.
  • the Abschlappitch 40, 41 are necessary to avoid edge beams.

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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)

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Hochdruckpumpe, insbesondere eine Radial- oder Reihenkolbenpumpe. Speziell betrifft die Erfindung das Gebiet der Brennstoffpumpen für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a high-pressure pump, in particular a radial or linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.

Aus der DE 10 2005 046 670 A1 ist eine Hochdruckpumpe für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine bekannt. Die bekannte Hochdruckpumpe weist ein Pumpengehäuse auf, in dem ein Pumpenelement angeordnet ist, das einen durch eine Antriebswelle in einer Hubbewegung angetriebenen Pumpenkolben umfasst. Der Pumpenkolben ist in einer Zylinderbohrung eines Teils des Pumpengehäuses verschiebbar geführt und begrenzt in dieser einen Pumpenarbeitsraum. Der Pumpenkolben stützt sich mittelbar über einen hohlzylinderförmigen Stößel an der Antriebswelle ab, wobei der Stößel in einer Bohrung eines Teils des Pumpengehäuses in Richtung der Längsachse des Pumpenkolbens verschiebbar geführt ist. Die Längsachse des Stößels ist im Wesentlichen identisch mit der Längsachse des Pumpenkolbens. Im Stößel ist indessen der Antriebswelle zugewandtem Endbereich ein Stützelement eingesetzt, in dem eine Rolle drehbar gelagert ist, die auf dem Nocken der Antriebswelle abrollt. Die Drehachse der Rolle ist zumindest annähernd parallel zur Drehachse der Antriebswelle. Das Stützelement weist auf seiner der Antriebswelle zugewandten Seite eine Vertiefung auf, in der die Rolle gelagert ist.From the DE 10 2005 046 670 A1 a high-pressure pump for a fuel injection device of an internal combustion engine is known. The known high-pressure pump has a pump housing, in which a pump element is arranged, which comprises a driven by a drive shaft in a stroke pump piston. The pump piston is slidably guided in a cylinder bore of a part of the pump housing and limited in this one pump working space. The pump piston is supported indirectly via a hollow cylindrical plunger on the drive shaft, wherein the plunger is slidably guided in a bore of a portion of the pump housing in the direction of the longitudinal axis of the pump piston. The longitudinal axis of the plunger is substantially identical to the longitudinal axis of the pump piston. In the plunger, however, the drive shaft facing end portion is a support member used in which a roller is rotatably mounted, which rolls on the cam of the drive shaft. The axis of rotation of the roller is at least approximately parallel to the axis of rotation of the drive shaft. The support member has on its side facing the drive shaft a recess in which the roller is mounted.

Die aus der DE 10 2005 046 670 A1 bekannte Hochdruckpumpe hat den Nachteil, dass die Rolle eng im Stößel geführt ist, so dass sich ein ungünstiges Laufverhalten der Rolle ergibt und Reibungskräfte und Verschleiß auftreten.The from the DE 10 2005 046 670 A1 known high-pressure pump has the disadvantage that the role is performed closely in the plunger, so that there is an unfavorable running behavior of the role and friction forces and wear occur.

Um das Laufverhalten der Rolle zu verbessern, ist es denkbar, dass eine gewisse Verschiebbarkeit der Rolle entlang ihrer Drehachse ermöglicht wird und außerdem eine von einer zylinderförmigen Form abweichende Ausgestaltung der Rolle gewählt ist. Hierdurch kann ein Kantenlauf der Rolle am Rollenschuh beziehungsweise an dem Nocken der Antriebswelle unter Belastung vermieden werden. Allerdings ergibt sich dadurch der Nachteil, dass auf Grund der von der zylinderförmigen Form abweichenden Ausgestaltung der Rolle die Reibung zwischen der Rolle und dem Rollenschuh zunimmt, weil auf Grund des größeren Spalts zwischen der Rolle und dem Rollenschuh die hydrodynamischen Eigenschaften verschlechtert sind. Hierdurch wird der Lauf der Rolle schwergängiger, was gegebenenfalls auch zu Triebwerksschäden führen kann.In order to improve the running behavior of the roller, it is conceivable that a certain displaceability of the roller along its axis of rotation is made possible and also a deviating from a cylindrical shape configuration of the roller is selected. hereby An edge run of the roller on the roller shoe or on the cam of the drive shaft can be avoided under load. However, this results in the disadvantage that due to the deviating from the cylindrical shape of the roller, the friction between the roller and the roller shoe increases, because due to the larger gap between the roller and the roller shoe, the hydrodynamic properties are deteriorated. As a result, the run of the role is stiff, which may possibly also lead to engine damage.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass ein Laufverhalten der Rolle an der Lauffläche des Nockens verbessert, und dass die Abschlappung der Lauffläche und die Rolle so ausgestaltet sind, dass in einer zentrierten Grundstellung der Rolle zwischen einem Endabschnitt der Rolle und der Lauffläche ein Spalt gebildet ist. Speziell kann die Hydrodynamik zwischen der Rolle und einem Rollenschuh verbessert und gleichzeitig ein vorteilhaftes Laufverhalten der Rolle an der Lauffläche des Nockens erzielt werden.The high-pressure pump according to the invention with the features of claim 1 has the advantage that a running behavior of the roller on the tread of the cam improves, and that the Abschlappung the tread and the roller are designed so that in a centered basic position of the roller between an end portion of the roller and the tread is formed a gap. Specifically, the hydrodynamics between the roller and a roller shoe can be improved and at the same time an advantageous running behavior of the roller on the tread of the cam can be achieved.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen der im Anspruch 1 angegebenen Hochdruckpumpe möglich.The measures listed in the dependent claims advantageous refinements of the claim 1 high-pressure pump are possible.

Vorteilhaft ist es, dass die Lauffläche im Bereich der Abschlappung konvex ausgestaltet ist. Außerdem ist es vorteilhaft, dass die Abschlappung der Lauffläche so ausgestaltet ist, dass auch in einer dezentrierten Stellung der Rolle zwischen dem Endabschnitt der Rolle und der Lauffläche ein Spalt gebildet ist. Hierdurch kann in Bezug auf einen Rollenschuh oder dergleichen, in dem die Rolle gelagert ist, ein konstant kleiner Spalt gewährleistet werden. Hierdurch kann durch die Abschlappung an der Nockenwelle die Rolle auf ihrer Bahn zentriert werden. Bei einem auftretenden Winkelfehler zwischen der Rolle und dem Nocken der Antriebswelle wird die Rolle durch die von der Anpresskraft aus der Druckerzeugung hervorgerufene Biegung der Rolle um den Nocken durch die Abschlappung geführt. Somit wird einem schrägen Nockenhochlauf der Rolle durch die Abschlappung entgegen gewirkt. Speziell kann somit ein Seitenanlauf der Rolle verhindert oder zumindest vermieden werden.It is advantageous that the tread is convex in the region of the Abschlappung. Moreover, it is advantageous that the Abschlappung of the tread is designed so that even in a decentered position of the roller between the end portion of the roller and the tread a gap is formed. As a result, with respect to a roller shoe or the like, in which the roller is mounted, a constantly small gap can be ensured. As a result, by the Abschlappung on the camshaft, the role can be centered on its path. In an occurring angular error between the roller and the cam of the drive shaft, the roller is guided by the bending of the roller caused by the pressing force from the pressure generation around the cam through the Abschlappung. Thus, an oblique cam run-up of the roll is counteracted by the Abschlappung. Specifically, thus a side start of the role can be prevented or at least avoided.

Ferner ist es hierbei vorteilhaft, dass der zwischen dem Endabschnitt der Rolle und der Lauffläche gebildete Spalt in einer dezentrierten Stellung der Rolle, in der die Rolle aus der zentrierten Grundstellung in Richtung der Abschlappung der Lauffläche verstellt ist, zumindest näherungsweise gleich groß ausgebildet ist wie in der zentrierten Grundstellung. Hierdurch kann bei einem gegebenen Winkelfehler zwischen dem Rollenschuh und dem Nocken stets eine rückstellende Kraft auf die Rolle ausgeübt werden, die die Rolle in die zentrierte Grundstellung zurückführt. Hierbei ist es ferner vorteilhaft, dass die Abschlappung der Lauffläche bis zu einer Stirnseite des Nockens ausgebildet ist.Furthermore, it is advantageous in this case that the gap formed between the end section of the roller and the running surface in a decentered position of the roller, in which the roller is adjusted from the centered basic position in the direction of the Abschlappung the tread, at least approximately the same size as in FIG the centered basic position. In this way, at a given angle error between the roller shoe and the cam always a restoring force are exerted on the roller, which returns the role in the centered home position. Here, it is also advantageous that the Abschlappung the tread is formed up to a front side of the cam.

Vorteilhaft ist es ferner, dass die Lauffläche einen mittleren Laufstreifen aufweist, der zumindest näherungsweise zylindermantelförmig ausgestaltet ist und dass die Abschlappung an den mittleren Laufstreifen angrenzt. Hierdurch wird in der zentrierten Grundstellung ein vorteilhaftes Laufverhalten zwischen der Rolle und dem Nocken erzielt. Ferner ist es vorteilhaft, dass ein Rollenschuh vorgesehen ist, in dem die Rolle gelagert ist, und dass der Rollenschuh eine gewisse Verschiebbarkeit der Rolle senkrecht zu einer Laufrichtung der Rolle an der Lauffläche ermöglicht. Die Rolle ist hierbei vorzugsweise im Wesentlichen als zylinderförmige Rolle ausgestaltet. Hierdurch kann zwischen dem Rollenschuh und der Rolle ein konstanter, kleiner Spalt auch bei einer Verschiebung der Rolle senkrecht zu der Laufrichtung gewährleistet werden. Hierdurch ergibt sich eine verbesserte Hydrodynamik zwischen der Rolle und dem Rollenschuh. Somit ergibt sich insgesamt ein günstiges Laufverhalten der Rolle.It is also advantageous that the tread has a central tread, which is designed at least approximately cylinder jacket-shaped and that the Abschlappung adjacent to the middle tread. As a result, an advantageous running behavior between the roller and the cam is achieved in the centered basic position. Further, it is advantageous that a roller shoe is provided, in which the roller is mounted, and that the roller shoe allows a certain displaceability of the roller perpendicular to a running direction of the roller on the tread. The role is preferably configured substantially as a cylindrical roller. As a result, between the roller shoe and the roller a constant, small gap can be ensured even with a displacement of the roller perpendicular to the direction. This results in an improved hydrodynamics between the roller and the roller shoe. Thus, overall results in a favorable running behavior of the role.

Vorteilhaft ist es auch, dass der Nocken an seiner Lauffläche eine weitere Abschlappung aufweist und dass die Abschlappung und die weitere Abschlappung bezüglich einer zentrierten Grundstellung der Rolle symmetrisch ausgestaltet sind. Hierbei ist es ferner vorteilhaft, dass die Abschlappung und die weitere Abschlappung so ausgestaltet sind, dass die Rolle in einer zentrierten Grundstellung geführt ist. Durch die Abschlappungen an dem Nocken wird somit die Rolle auf ihrer Bahn zentriert. Einem schrägen Nockenhochlauf der Rolle wird somit entgegen gewirkt. Dadurch ist zu beiden Seiten ein Seitenanlauf der Laufrolle verhindert oder zumindest vermieden.It is also advantageous that the cam has a further Abschlappung on its tread and that the Abschlappung and further Abschlappung are configured symmetrically with respect to a centered basic position of the role. Here, it is also advantageous that the Abschlappung and further Abschlappung are designed so that the roller is guided in a centered basic position. Due to the Abschlappungen on the cam thus the role is centered on its path. An oblique cam run-up of the roller is thus counteracted. As a result, a lateral start of the roller is prevented or at least avoided on both sides.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung anhand der beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 eine Hochdruckpumpe in einer schematischen, axialen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung und
  • Fig. 2 den in Fig. 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe des Ausführungsbeispiels der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with corresponding reference numerals. It shows:
  • Fig. 1 a high pressure pump in a schematic, axial sectional view according to an embodiment of the invention and
  • Fig. 2 the in Fig. 1 labeled II section of the high-pressure pump of the embodiment of the invention.

Ausführungsformen der ErfindungEmbodiments of the invention

Fig. 1 zeigt eine Hochdruckpumpe 1 in einer schematischen, axialen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung. Die Hochdruckpumpe 1 kann insbesondere als Radial- oder Reihenkolbenpumpe ausgestaltet sein. Speziell eignet sich die Hochdruckpumpe 1 als Brennstoffpumpe für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen. Ein bevorzugter Einsatz der Hochdruckpumpe 1 besteht für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste, einem sogenannten Common-Rail, das Dieselbrennstoff unter hohem Druck speichert. Die erfindungsgemäße Hochdruckpumpe 1 eignet sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows a high pressure pump 1 in a schematic, axial sectional view according to an embodiment of the invention. The high pressure pump 1 can be configured in particular as a radial or inline piston pump. Specifically, the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the high pressure pump 1 is for a fuel injection system with a fuel rail, a so-called common rail that stores diesel fuel under high pressure. However, the high-pressure pump 1 according to the invention is also suitable for other applications.

Die Hochdruckpumpe 1 weist ein mehrteiliges Pumpengehäuse 2 auf. Hierbei umfasst das Pumpengehäuse 2 ein Gehäuseteil 3 und einen mit dem Gehäuseteil 3 verbundenen Flansch 4. Ferner ist ein Zylinderkopf 5 vorgesehen, der mit dem Gehäuseteil 3 verbunden ist.The high-pressure pump 1 has a multipart pump housing 2. In this case, the pump housing 2 comprises a housing part 3 and a flange 4 connected to the housing part 3. Furthermore, a cylinder head 5 is provided, which is connected to the housing part 3.

In dem Pumpengehäuse 2 ist eine Antriebswelle 6 angeordnet. Die Antriebswelle 6 umfasst einen Nocken 7. Der Nocken 7 kann auch als Mehrfachnocken ausgestaltet sein. Ferner kann der Nocken 7 auch als exzentrischer Abschnitt der Antriebswelle 6 ausgestaltet sein. In dem Gehäuseteil 3 ist eine Lagerstelle 8 ausgebildet. Ferner ist an dem Flansch 4 eine weitere Lagerstelle 9 vorgesehen. Die Antriebswelle 6 ist an den Lagerstellen 8, 9 gelagert.In the pump housing 2, a drive shaft 6 is arranged. The drive shaft 6 includes a cam 7. The cam 7 can also be configured as a multiple cam. Furthermore, the cam 7 can also be designed as an eccentric portion of the drive shaft 6. In the housing part 3, a bearing 8 is formed. Furthermore, a further bearing 9 is provided on the flange 4. The drive shaft 6 is mounted on the bearings 8, 9.

Im Betrieb der Hochdruckpumpe 1 rotiert die Antriebswelle 6 um ihre Drehachse 10. Die Lagerstellen 8, 9 sind bezüglich der Drehachse 10 voneinander beabstandet und an verschiedenen Seiten des Nockens 7 angeordnet.During operation of the high pressure pump 1, the drive shaft 6 rotates about its axis of rotation 10. The bearings 8, 9 are spaced from each other with respect to the axis of rotation 10 and arranged on different sides of the cam 7.

Die Hochdruckpumpe 1 weist eine Pumpenbaugruppe 15 auf. Die Hochdruckpumpe 1 kann auch mehrere Pumpenbaugruppen aufweisen. Die Pumpenbaugruppe 15 ist mittels des Nockens 7 der Antriebswelle 6 antreibbar. Sofern die Hochdruckpumpe 1 weitere Pumpenbaugruppen aufweist, können diese zusammen mit der Pumpenbaugruppe 15 von dem Nocken 7 angetrieben sein. Möglich ist es auch, dass an der Antriebswelle 6 zumindest ein weiterer Nocken vorgesehen ist, der entsprechend dem Nocken 7 zum Antreiben zumindest einer Pumpenbaugruppe dient. Je nach Ausgestaltung kann dadurch eine Radial- oder Reihenkolbenpumpe realisiert werden.The high-pressure pump 1 has a pump assembly 15. The high-pressure pump 1 may also have a plurality of pump assemblies. The pump assembly 15 can be driven by means of the cam 7 of the drive shaft 6. If the high-pressure pump 1 has further pump assemblies, these may be driven by the cam 7 together with the pump assembly 15. It is also possible that at least one further cam is provided on the drive shaft 6, which serves according to the cam 7 for driving at least one pump assembly. Depending on the configuration, a radial or series piston pump can thereby be realized.

Das Gehäuseteil 3 des Pumpengehäuses 2 weist eine Bohrung 16 auf. An dem Zylinderkopf 5 ist ein Ansatz 17 ausgebildet, der in die Bohrung 16 des Gehäuseteils 3 ragt. Die Pumpenbaugruppe 15 ist im Bereich des Ansatzes 17 und der Bohrung 16 vorgesehen. Hierfür weist der Ansatz 17 eine Zylinderbohrung 18 auf, in der ein Pumpenkolben 19 geführt ist. Der Pumpenkolben 19 begrenzt hierbei einen Pumpenarbeitsraum 20 in der Zylinderbohrung 18. Über ein Einlassventil 21 kann Brennstoff in den Pumpenarbeitsraum 20 gelangen. Ferner ist ein Auslassventil 22 vorgesehen, über das Brennstoff aus dem Pumpenarbeitsraum 20 in eine Verbindungsleitung 23 gefördert werden kann. Die Verbindungsleitung 23 führt beispielsweise zu einem Common-Rail.The housing part 3 of the pump housing 2 has a bore 16. On the cylinder head 5, a projection 17 is formed, which projects into the bore 16 of the housing part 3. The pump assembly 15 is provided in the region of the projection 17 and the bore 16. For this purpose, the approach 17 has a cylinder bore 18 in which a pump piston 19 is guided. In this case, the pump piston 19 limits a pump working chamber 20 in the cylinder bore 18. Fuel can enter the pump working chamber 20 via an inlet valve 21. Furthermore, an outlet valve 22 is provided, via which fuel can be conveyed out of the pump working chamber 20 into a connecting line 23. The connecting line 23 leads, for example, to a common rail.

Die Zylinderbohrung 18 weist eine Achse 24 auf, die zumindest näherungsweise auf die Drehachse 10 zeigt und senkrecht zu der Drehachse 10 orientiert ist. Der Pumpenkolben 19 ist entlang der Achse 24 verschiebbar, wie es durch den Doppelpfeil 25 veranschaulicht ist.The cylinder bore 18 has an axis 24 which is at least approximately pointing to the axis of rotation 10 and oriented perpendicular to the axis of rotation 10. The pump piston 19 is slidable along the axis 24, as illustrated by the double arrow 25.

Die Pumpenbaugruppe 15 weist außerdem einen hohlzylinderförmigen Stößelkörper 26 auf, der in der Bohrung 16 geführt ist. Ein in den Stößelkörper 26 eingesetztes Mitnahmeelement 27 hintergreift einen Bund 28 des Pumpenkolbens 19. Hierbei wird das Mitnahmeelement 27 von einer Stößelfeder 29 in Richtung auf den Nocken 7 beaufschlagt. Bei einer Bewegung des Stößelkörpers 26 wird somit der Pumpenkolben 19 mitgenommen.The pump assembly 15 also has a hollow cylindrical plunger body 26 which is guided in the bore 16. An inserted into the plunger body 26 driving element 27 engages behind a collar 28 of the pump piston 19. Here, the driving element 27 is acted upon by a plunger spring 29 in the direction of the cam 7. During a movement of the plunger body 26 thus the pump piston 19 is taken.

In den Stößelkörper 26 ist außerdem ein Rollenschuh 30 eingesetzt. Der Bund 28 des Pumpenkolbens 19 liegt an dem Rollenschuh 30 an. In dem Rollenschuh 30 ist eine Rolle 31 gelagert, die als Laufrolle 31 ausgestaltet ist. Die Rolle 31 ist hierbei zumindest im Wesentlichen zylinderförmig ausgestaltet. Hierdurch ergibt sich eine vorteilhafte Führung der Rolle 31 in dem Rollenschuh 30. Insbesondere ergibt sich eine vorteilhafte Hydrodynamik zwischen der Rolle 31 und dem Rollenschuh 30. Es besteht nämlich einer großer Bereich mit einem konstanten kleinen Spalt zwischen der Rolle 31 und dem Rollenschuh 30. Somit ist eine vorteilhafte Lagerung der Rolle 31 in dem Rollenschuh 30 gewährleistet.In the plunger body 26, a roller shoe 30 is also used. The collar 28 of the pump piston 19 abuts against the roller shoe 30. In the roller shoe 30, a roller 31 is mounted, which is designed as a roller 31. The roller 31 is in this case at least substantially cylindrical. This results in an advantageous guidance of the roller 31 in the roller shoe 30. In particular, there is an advantageous hydrodynamics between the roller 31 and the roller shoe 30. Namely, there is a large area with a constant small gap between the roller 31 and the roller shoe 30. Thus an advantageous storage of the roller 31 is ensured in the roller shoe 30.

Der Nocken 7 weist eine Stirnseite 32, die der Lagerstelle 9 zugewandt ist, und eine weitere Stirnseite 33 auf, die der Lagerstelle 8 zugewandt ist. Die Stirnseiten 32, 33 sind voneinander abgewandt. Außerdem weist der Nocken 7 eine Lauffläche 34 auf. Im Betrieb läuft die Rolle 31 beispielsweise in einer Laufrichtung 35 entlang der Lauffläche 34. Hierbei weist die Lauffläche 34 einen mittleren Laufstreifen 36 auf, an dem die Lauffläche 34 zumindest näherungsweise zylindermantelförmig ausgestaltet ist. Hierdurch ist eine zentrierte Grundstellung der Rolle 31 an der Lauffläche 34 gegeben, die in der Fig. 1 gezeigt ist. Die Rolle 31 rotiert hierbei um ihre Achse 37.The cam 7 has an end face 32, which faces the bearing point 9, and a further end face 33, which faces the bearing point 8. The end faces 32, 33 are remote from each other. In addition, the cam 7 has a running surface 34. In operation, the roller 31 runs, for example, in a running direction 35 along the running surface 34. In this case, the running surface 34 has a central tread 36 on which the running surface 34 is configured at least approximately in the form of a cylinder jacket. As a result, a centered basic position of the roller 31 is given to the tread 34, in the Fig. 1 is shown. The roller 31 rotates about its axis 37.

Wenn die Antriebswelle 6 um ihre Drehachse 10 rotiert, dann läuft die Rolle 31 entlang der Lauffläche 34, so dass entsprechend dem Nockenhub des Nockens 7 eine Betätigung des Pumpenkolbens 19 der Pumpenbaugruppe 15 erfolgt. Hierdurch wird abwechselnd Brennstoff in den Pumpenarbeitsraum 20 angesaugt und anschließend unter hohem Druck über die Verbindungsleitung 23 gefördert.When the drive shaft 6 rotates about its axis of rotation 10, then the roller 31 runs along the running surface 34, so that according to the cam lift of the cam 7, an actuation of the pump piston 19 of the pump assembly 15 takes place. As a result, fuel is alternately sucked into the pump working chamber 20 and then conveyed under high pressure via the connecting line 23.

Die Ausgestaltung der Hochdruckpumpe 1 ist im Folgenden auch unter Bezugnahme auf die Fig. 2 im weiteren Detail beschrieben.The configuration of the high-pressure pump 1 is below also with reference to the Fig. 2 described in further detail.

Fig. 2 zeigt den in Fig. 1 mit II bezeichneten Ausschnitt der Hochdruckpumpe 1 des Ausführungsbeispiels, wobei der Rollenschuh 30, die Rolle 31 und ausschnittsweise der Nocken 7 dargestellt sind. Der Nocken 7 weist an seiner Lauffläche 34 eine Abschlappung 40 und eine weitere Abschlappung 41 auf. Hierbei erstreckt sich die Abschlappung 40 bis zu der Stirnseite 32. Die weitere Abschlappung 41 erstreckt sich bis zu der weiteren Stirnseite 33. Ferner grenzen die Abschlappungen 40, 41 zu beiden Seiten an den mittleren Laufstreifen 36 der Lauffläche 34 an. In diesem Ausführungsbeispiel erstreckt sich somit der mittlere Laufstreifen 36 zusammen mit den beiden Abschlappungen 40, 41 über die gesamte Lauffläche 34 des Nockens 7. Fig. 2 shows the in Fig. 1 With II designated section of the high-pressure pump 1 of the embodiment, wherein the roller shoe 30, the roller 31 and parts of the cam 7 are shown. The cam 7 has on its tread 34 a Abschlappung 40 and a further Abschlappung 41. In this case, the Abschlappung 40 extends to the end face 32. The further Abschlappung 41 extends to the other end face 33. Further, the Abschlappungen 40, 41 adjoin on both sides of the central tread 36 of the tread 34 at. In this embodiment, therefore, the middle tread 36 extends together with the two Abschlappungen 40, 41 over the entire running surface 34 of the cam. 7

Die Abschlappungen 40, 41 sind als konvexe Abschlappungen 40, 41 ausgestaltet. In Bezug auf die zumindest näherungsweise zylinderförmig ausgestaltete Rolle 31 sind durch die Abschlappungen 40, 41 kleine Spalte 42, 43 zwischen der Rolle 31 und der Lauffläche 34 gebildet. Die Spalte 42, 43 betreffen hierbei einen Endabschnitt 44 und einen weiteren Endabschnitt 45 der Rolle 31. Ein Mittelstück 46 der Rolle 31 liegt hingegen an dem mittleren Laufstreifen 36 an.The Abschlappungen 40, 41 are configured as convex Abschlappungen 40, 41. With respect to the at least approximately cylindrical roller 31 are formed by the Abschlappungen 40, 41 small gaps 42, 43 between the roller 31 and the tread 34. The gaps 42, 43 in this case relate to an end portion 44 and a further end portion 45 of the roller 31. A center piece 46 of the roller 31, however, is applied to the middle tread 36 at.

Somit ist in der in den Fig. 1 und 2 dargestellten zentrierten Grundstellung der Rolle 31 ein vorteilhaftes Abrollen der Rolle 31 an dem mittleren Laufstreifen 36 der Lauffläche 34 gewährleistet.Thus, in the in the Fig. 1 and 2 illustrated centered basic position of the roller 31 ensures an advantageous rolling of the roller 31 on the middle tread 36 of the tread 34.

Im Betrieb der Hochdruckpumpe 1 kann es zu einem Winkelfehler mit einem Winkel 47 kommen. Wenn ein Winkelfehler auftritt, dann ergibt sich zwischen dem Rollenschuh 30 mit der Rolle 31 und dem Nocken 7 beziehungsweise der Achse 24 ein nicht verschwindender Winkel 47. Für einen zuverlässigen Betrieb der Hochdruckpumpe 1 kann solch ein Spiel auch erforderlich sein.During operation of the high-pressure pump 1, an angle error can occur at an angle 47. If an angular error occurs, then results between the roller shoe 30 with the roller 31 and the cam 7 and the axis 24, a non-vanishing angle 47. For a reliable operation of the high-pressure pump 1, such a game may also be required.

Durch die Ausgestaltung des Nockens 7 mit den Abschlappungen 40, 41 ist eine Rückstellung des Systems in die Grundstellung gewährleistet. Hierbei wirkt bei einem Winkelfehler eine rückstellende Kraft in die Grundstellung. Bei einem nicht verschwindenden Winkel 47 wird die Rolle 31 nämlich durch die von der Anpresskraft aus der Druckerzeugung hervorgerufene Biegung der Rolle 31 um den Nocken 7 durch die Abschlappungen 40, 41 geführt. Es wird somit bei einem schrägen Nockenhochlauf der Rolle 31 durch die Abschlappungen 40, 41 eine rückstellende Kraft auf die Rolle 31 und somit auch den Rollenschuh 30 ausgeübt. Hierdurch wird einem schrägen Nockenhochlauf der Rolle 31 entgegen gewirkt. Dies wirkt je nach Ausgestaltung der Hochdruckpumpe 1 auch einem möglichen Seitenanlauf der Rolle 31 entgegen.Due to the design of the cam 7 with the Abschlappungen 40, 41 a provision of the system is guaranteed in the normal position. In the case of an angle error, a restoring force acts in the basic position. At a non-vanishing angle 47, the roller 31 is namely guided by the bending of the roller 31 about the cam 7 by the Abschlappungen 40, 41 caused by the pressure force from the generation of pressure. It is thus at an oblique cam run-up of the roller 31 through the Abschlappungen 40, 41 a restoring force on the roller 31 and thus also the roller shoe 30 is exercised. As a result, an oblique cam run-up of the roller 31 is counteracted. Depending on the configuration of the high-pressure pump 1, this also counteracts a possible lateral start-up of the roller 31.

Da bei dieser Ausgestaltung eine vorteilhafte Führung der Rolle 31 in dem Rollenschuh 30 gewährleistet ist, ergibt sich in Kombination mit der vorteilhaften Führung der Rolle 31 an der Lauffläche 34 ein optimiertes Laufverhalten der Rolle 31 im Betrieb.Since an advantageous guidance of the roller 31 in the roller shoe 30 is ensured in this embodiment, in combination with the advantageous guidance of the roller 31 on the running surface 34, an optimized running behavior of the roller 31 during operation results.

Im Unterschied zu einer denkbaren Ausgestaltung, bei der Abschlappungen an der Rolle 31 vorgesehen sind, werden Spalte zwischen dem Rollenschuh 30 und der Rolle 31 vermieden. Somit bleibt bei der Ausgestaltung des Ausführungsbeispiels die Hydrodynamik zwischen dem Rollenschuh 30 und der Rolle 31 erhalten. Eine schwergängige Laufrolle 31 wird von vornherein vermieden, so dass auch Triebwerksschäden oder dergleichen verhindert sind. Kantenträger in Bezug auf den Rollenschuh 30 beziehungsweise den Nocken 7 unter Belastung sind dabei vermieden.In contrast to a conceivable embodiment in which Abschlappungen are provided on the roller 31, gaps between the roller shoe 30 and the roller 31 are avoided. Thus, in the embodiment of the embodiment, the hydrodynamics between the roller shoe 30 and the roller 31 is maintained. A stiff roller 31 is avoided from the outset, so that engine damage or the like are prevented. Edge bearer with respect to the roller shoe 30 and the cam 7 under load are avoided.

Die Abschlappungen 40, 41 sind notwendig, um Kantenträger zu vermeiden. Dadurch, dass die Abschlappungen an der Nockenwelle liegen und nicht an der Rolle 31, kann die Hydrodynamik zwischen der Rolle 31 und dem Rollenschuh 30 perfektioniert werden.The Abschlappungen 40, 41 are necessary to avoid edge beams. The fact that the Abschlappungen lie on the camshaft and not on the roller 31, the hydrodynamics between the roller 31 and the roller shoe 30 can be perfected.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (9)

  1. High-pressure pump (1), in particular radial or in-line piston pump for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having at least one pump assembly (15) and one drive shaft (6) which has at least one cam (7) assigned to the pump assembly (15), wherein the pump assembly (15) has a roller (31) which runs on a running surface (34) of the cam (7),
    characterized
    in that the cam (7) has, on its running surface (34), at least one decline (40) such that, in a centred basic position of the roller (31), a gap (42) is formed between an end section (44) of the roller (31) and the running surface (34) such that, in the event of the roller (31) running obliquely up the cam, a restoring force is exerted on the roller (31) by means of the decline (40).
  2. High-pressure pump according to Claim 1,
    characterized
    in that the running surface (34) is of convex design in the region of the decline (40).
  3. High-pressure pump according to Claim 1 or 2,
    characterized
    in that the decline (40) of the running surface (34) is designed such that, even in an eccentric position of the roller (31), a gap (42) is formed between the end section (44) of the roller (31) and the running surface (34).
  4. High-pressure pump according to Claim 3,
    characterized
    in that the gap (42) formed between the end section (44) of the roller (31) and the running surface (34) is at least approximately of the same size in an eccentric position of the roller (31), in which the roller (31) has been adjusted out of the centred basic position in the direction of the decline (40) of the running surface (34), as in the centred basic position.
  5. High-pressure pump according to one of Claims 1 to 4,
    characterized
    in that the decline (40) of the running surface (34) is formed as far as a face side (32) of the cam (7).
  6. High-pressure pump according to one of Claims 1 to 5,
    characterized
    in that the running surface (34) has a central running strip (36) which is at least approximately of cylindrical-shell-shaped design, and in that the decline (40) adjoins the central running strip (36).
  7. High-pressure pump according to one of Claims 1 to 6,
    characterized
    in that a roller shoe (30) is provided in which the roller (31) is mounted, and in that the roller shoe (30) permits a displaceability of the roller (31), perpendicular to a running direction (35) of the roller (31), on the running surface (34).
  8. High-pressure pump according to one of Claims 1 to 7,
    characterized
    in that the cam (7) has a further decline (41) on its running surface (34), and in that the decline (40) and the further decline (41) are of symmetrical design with respect to a centred basic position of the roller (31).
  9. High-pressure pump according to Claim 8,
    characterized
    in that the decline (40) and the further decline (41) are designed such that the roller (31) is guided into a centred basic position.
EP11709037.3A 2010-04-15 2011-03-02 High pressure pump Not-in-force EP2558707B1 (en)

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DE102010027792A DE102010027792A1 (en) 2010-04-15 2010-04-15 high pressure pump
PCT/EP2011/053108 WO2011128151A1 (en) 2010-04-15 2011-03-02 High-pressure pump

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EP2558707A1 EP2558707A1 (en) 2013-02-20
EP2558707B1 true EP2558707B1 (en) 2018-05-16

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EP (1) EP2558707B1 (en)
JP (1) JP5395308B2 (en)
CN (1) CN102939456B (en)
DE (1) DE102010027792A1 (en)
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DE102013212047A1 (en) * 2013-06-25 2015-01-08 Robert Bosch Gmbh Pump device, in particular high-pressure fuel pump device for a fuel injection device
US9835123B2 (en) * 2015-01-13 2017-12-05 Roller Bearing Company Of America, Inc. Roller for a fuel pump actuator
WO2022036230A1 (en) * 2020-08-14 2022-02-17 Cummins Inc. Sliding cam follower

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DE102010027792A1 (en) 2011-10-20
CN102939456B (en) 2015-04-08
WO2011128151A1 (en) 2011-10-20
JP2013524095A (en) 2013-06-17
JP5395308B2 (en) 2014-01-22
CN102939456A (en) 2013-02-20
EP2558707A1 (en) 2013-02-20

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