EP2430303B1 - High pressure pump - Google Patents

High pressure pump Download PDF

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Publication number
EP2430303B1
EP2430303B1 EP10709736.2A EP10709736A EP2430303B1 EP 2430303 B1 EP2430303 B1 EP 2430303B1 EP 10709736 A EP10709736 A EP 10709736A EP 2430303 B1 EP2430303 B1 EP 2430303B1
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EP
European Patent Office
Prior art keywords
roller
cam
running
running roller
radius
Prior art date
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Application number
EP10709736.2A
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German (de)
French (fr)
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EP2430303A1 (en
Inventor
Andreas Dutt
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02Pumps 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
    • F02M59/10Pumps 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
    • F02M59/102Mechanical drive, e.g. tappets or cams
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M41/00Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/10Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor
    • F02M41/12Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor
    • F02M41/123Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined pump pistons acting as the distributor the pistons rotating to act as the distributor characterised by means for varying fuel delivery or injection timing
    • F02M41/128Varying injection timing by angular adjustment of the face-cam or the rollers support
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06Pumps peculiar thereto
    • F02M45/063Delivery stroke of piston being divided into two or more parts, e.g. by using specially shaped cams
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, 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
    • F02M59/445Selection of particular materials
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/02Fuel-injection apparatus having means for reducing wear

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.
  • the known high-pressure pump has a multipart pump housing, in which at least one pump element is arranged.
  • the pump element comprises a driven by a drive shaft in a stroke pump piston which is slidably guided in a cylinder bore of a portion of the pump housing and defines a pump working space therein.
  • the drive shaft has a cam, wherein the pump piston is driven by the cam of the drive shaft in the radial direction to a rotational axis of the drive shaft.
  • a plunger is arranged, via which the pump piston is supported via a roller on the cam of the drive shaft.
  • a support element is used, in which the roller is rotatably mounted, wherein the roller rolls on the cam of the drive shaft.
  • the axis of rotation of the roller is in this case approximately parallel to the axis of rotation of the drive shaft.
  • a high pressure pump having a pump assembly and a drive shaft having a cam associated with the pump assembly.
  • the pump assembly has a roller having a roller surface, wherein the Roller is arranged on a running surface of the cam.
  • the shape of the tread of the cam is determined so that the maximum allowable Hertzian pressure between the roller surface of the roller and the tread of the cam is not exceeded at the given load of the pump assembly.
  • the rolling resistance of the roller and the cam is not defined.
  • roller tappet which can be used to drive an injection pump.
  • the roller tappet has a roller having a roller surface, wherein the roller is arranged on a running surface of a cam of a drive shaft.
  • the roller surface and the tread of the cam are formed crowned to ensure an unrolling of the roller to the cam rolling the roller on the tread of the cam. Information on the rolling resistance of the roller and the cam are not available.
  • the high-pressure pump according to the invention with the features of claim 1 has the advantage that a reliable operation, in particular an improved durability of the cam and / or the roller, is achieved.
  • the cam and the roller are designed to be improved with respect to the swelling stress occurring during operation.
  • the expression of a critical threshold voltage for the roller and the cam during operation can be interpreted equally critical in different geometries of the roller and the cam.
  • an optimization in terms of a yield strength of the roller and a yield point of the cam is possible.
  • the Hertzian pressure on the roller surface of the roller is the same as the Hertzian pressure on the tread of the cam.
  • the Hertzian pressure must in each case be smaller than the yield strength of the roller or of the cam.
  • the fatigue of the two components roller and cam can be optimized by the adapted design of the roller on the cam.
  • the radius of the roller is smaller than the radius of curvature of the cam at the location of the running surface on which the roller rests in a top dead center of the pump assembly and in that the roller has at least one bore extending at least partially in the direction of a rotation axis the roller extends.
  • the bore with respect to the axis of rotation of the roller is at least substantially configured as an axial or at least substantially coaxial bore and / or that the bore is configured as a through hole extending from one side of the roller to another side of the roller. In this way, a reduction in the stiffness of the roller in the region of its roller surface can be achieved with different geometries at top dead center.
  • the radius of the roller is smaller than the radius of curvature of the cam at the location of the tread on which the roller rests in a top dead center of the pump assembly, and that at least one compressive residual stress of the roller is increased at its roller surface.
  • the roller surface of the roller case hardened and / or shot peened and / or rolled and / or nitrided and / or nitrocarburized. In this way, the rolling resistance of the roller can be increased by introducing compressive residual stress at the surface at different geometries of the roller and the cam at top dead center. As a result, an advantageous adaptation of the roller to the cam is possible.
  • Fig. 1 shows a high pressure pump 1 in a schematic, axial sectional view according to a first embodiment of the invention.
  • the high-pressure pump 1 can serve in particular as a radial or series piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the high-pressure pump 1 is suitable for a fuel injection system with a 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 multi-part housing 2.
  • the housing 2 consists of the housing parts 3, 4, 5, wherein the housing part 3 is a base body, the housing part 4 is a cylinder head and the housing part 5 is a fixed to the base body 3 flange.
  • the high-pressure pump 1 has a drive shaft 6 which is mounted at bearing points 7, 8 in the housing parts 3, 5. Between the bearings 7, 8, the drive shaft 6 has a cam 9.
  • the cam 9 is designed in this embodiment as a double cam.
  • the cam 9 can also be configured as a single or as another multiple cam.
  • the housing part 3 of the high-pressure pump 1 has a guide bore 12, in which a pump assembly 13 is arranged.
  • the cam 9 is associated with the pump assembly 13.
  • a plurality of pump assemblies 13 may be provided corresponding pump assemblies.
  • Such pump assemblies may be associated with the cam 9 or another cam corresponding to the cam 9.
  • a radial or piston pump can be realized.
  • the designed as a cylinder head housing part 4 has a projection 14 which extends into the guide bore 12.
  • the projection 14 has a cylinder bore 15 in which a piston 16 is slidably guided in the direction of an axis 17 of the guide bore 12, as illustrated by a double arrow 18.
  • the piston 16 defines a pump working space 19 in the cylinder bore 15.
  • an inlet valve 20 provided on the housing part 4 fuel from a fuel passage 21 can be introduced into the pump working space 19.
  • an outlet valve 22 is provided on the housing part 4, can be guided through the fuel under high pressure from the pump working chamber 19 to a fuel passage 13.
  • the fuel channel 13 may, for example, be connected to a common rail in order to guide fuel under high pressure to the common rail.
  • the pump assembly 13 has a roller 25 which is received by a roller shoe 26.
  • the roller shoe 26 is inserted in a substantially hollow cylindrical plunger body 27.
  • the plunger body 27 is connected to a disc-shaped driving element 28, which surrounds the piston 16 above a collar 29 of the piston 16.
  • a piston spring 30 is provided which on the plunger body 27 and / or the driving element 28 acts and thus acts on the plunger body 27 together with the piston 16 in the direction of the roller 25 with a certain spring force.
  • the drive shaft 6 rotates about an axis 31. Further, the roller 25 runs on the running surface 10 of the cam 9 from.
  • An axis of rotation 32 of the roller 25 is in this case oriented at least approximately parallel to the axis 31 of the drive shaft 6.
  • the roller 25 has a roller surface 35. The roller 25 rolls with its roller surface 35 in operation on the running surface 10 of the cam 9 from.
  • the high-pressure pump 1 of the embodiment is hereinafter also with reference to the Fig. 2 described in further detail.
  • Fig. 2 shows an excerpted section through the in Fig. 1 illustrated high pressure pump 1 along the designated II cutting line.
  • the roller 25 rests with its roller surface 35 at a point 36 of the tread 10 of the cam 9. In this position or in the region of this position, the highest stress of the roller 25 and the cam 9 occurs. In this case, the maximum delivery stroke of the piston 16 of the pump assembly 13 is reached, so that the maximum pressure which can be generated by the high-pressure pump 1 exists in the pump working chamber 19. This affects a correspondingly large force F.
  • the roller 25 and the cam 9 may be made of hardened high strength tool steels.
  • a geometric configuration and a roller material of the roller 25 and a geometric configuration of the cam and a cam material of the cam 9 are selected so that a Wälzbe bulk sadness the roller 25 and a Wälzbe bulkles of the cam 9 on the tread 10 of the cam 9 are at least approximately the same size.
  • especially the rolling load capacity of the cam 9 at the point 36 of its tread 10 is relevant, since a maximum rolling load of the cam 9 occurs here.
  • the point 37 is arranged with respect to the axis 31 of the drive shaft 6 opposite to the point 36 on the tread 10.
  • the roller 35 is designed at least approximately cylindrical.
  • the roller 25 has a radius 38 with respect to its roller surface 35.
  • the cam 9 with respect to its tread 10 has a circumferentially varying radius of curvature. Since the highest rolling load of the cam 9 in the areas of the points 36, 37 occurs, a radius of curvature 39 at the point 36 is relevant, where the roller 25 abuts the tread 10 at the top dead center of the pump assembly 13. For the location 37, this results in a corresponding radius of curvature 40, which is equal to the radius of curvature 39.
  • the radius 38 of the roller 25 may be smaller or larger than the radius of curvature 39 of the cam 9.
  • the swelling stress has an even greater effect, the smaller the radius 38 of the roller 25 or the radius of curvature 39 of the cam 9.
  • the component becomes 25, 29 more heavily loaded, which has the smaller radius 38 or radius of curvature 39.
  • the critical threshold voltage for both components 9, 25 is designed to be equally critical with regard to the permissible rolling load. Examples of possible interpretations are described further below.
  • the roller has at least one bore 41.
  • a bore 41 allows a reduction in the rigidity of the roller 25, in particular in the region of its roller surface 35.
  • the bore 41 is preferably designed as an axial or coaxial bore 41.
  • the bore 41 is configured as an axial bore which extends along the axis of rotation 32 of the roller 25.
  • the bore 41 is configured as a through hole 41 in this embodiment.
  • the bore 41 extends from one side 42 of the roller 25 to another side 43 of the roller 25, which faces away from the side 42.
  • the roller 25 can be processed in the region of its roller surface 35. Specifically, case hardening of the roller surface 35, shot peening of the roller surface 35, rolling of the roller surface 35, nitriding of the roller surface 35 or even nitrocarburizing of the roller surface 35 are possible. In this way, the rolling resistance of the roller 25, in particular the roller surface 35 of the roller 25, can be increased by introducing compressive residual stresses on the roller surface 35.
  • the modulus of elasticity of the pulley material constituting the pulley 25 is greater than the modulus of elasticity of the cam material from which the pulley 25 Cam 9 is formed at least on its tread 10.
  • a load compensation is possible to achieve the same or at least a comparable load for both the roller 25 and the cam 9. It is also possible to edit, especially one Surface treatment of the cam 9. This may be carried out according to a surface treatment of the roller surface 35 of the roller 25.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (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 Brennstoffeinspritzeinrichtung einer Brennkraftmaschine bekannt. Die bekannte Hochdruckpumpe weist ein mehrteiliges Pumpengehäuse auf, in dem wenigstens ein Pumpenelement angeordnet ist. Das Pumpenelement umfasst einen durch eine Antriebswelle in einer Hubbewegung angetriebenen Pumpenkolben, der in einer Zylinderbohrung eines Teils des Pumpengehäuses verschiebbar geführt ist und in dieser einen Pumpenarbeitsraum begrenzt. Hierbei weist die Antriebswelle einen Nocken auf, wobei der Pumpenkolben durch den Nocken der Antriebswelle in radialer Richtung zu einer Drehachse der Antriebswelle angetrieben wird. Zwischen dem Pumpenkolben und dem Nocken der Antriebswelle ist ein Stößel angeordnet, über den sich der Pumpenkolben über eine Rolle am Nocken der Antriebswelle abstützt. In den Stößel ist ein Stützelement eingesetzt, in dem die Rolle drehbar gelagert ist, wobei die Rolle auf dem Nocken der Antriebswelle abrollt. Die Drehachse der Rolle ist hierbei annähernd parallel zur Drehachse der Antriebswelle.From the DE 10 2005 046 670 A1 a high pressure pump for a fuel injector of an internal combustion engine is known. The known high-pressure pump has a multipart pump housing, in which at least one pump element is arranged. The pump element comprises a driven by a drive shaft in a stroke pump piston which is slidably guided in a cylinder bore of a portion of the pump housing and defines a pump working space therein. Here, the drive shaft has a cam, wherein the pump piston is driven by the cam of the drive shaft in the radial direction to a rotational axis of the drive shaft. Between the pump piston and the cam of the drive shaft, a plunger is arranged, via which the pump piston is supported via a roller on the cam of the drive shaft. In the plunger, a support element is used, in which the roller is rotatably mounted, wherein the roller rolls on the cam of the drive shaft. The axis of rotation of the roller is in this case approximately parallel to the axis of rotation of the drive shaft.

Die aus der DE 10 2005 046 670 A1 bekannte Hochdruckpumpe hat den Nachteil, dass im Betrieb eine schwellende Beanspruchung des Nockens und der Laufrolle auftritt, die zu einer Materialermüdung führt.The from the DE 10 2005 046 670 A1 known high pressure pump has the disadvantage that in operation a swelling stress of the cam and the roller occurs, which leads to a material fatigue.

Durch die GB 896 030 A ist eine Hochdruckpumpe bekannt mit einer Pumpenbaugruppe und einer Antriebswelle, die einen der Pumpenbaugruppe zugeordneten Nocken aufweist. Die Pumpenbaugruppe weist eine Laufrolle auf, die eine Rollenoberfläche aufweist, wobei die Laufrolle an einer Lauffläche des Nockens angeordnet ist. Die Form der Lauffläche des Nockens ist so bestimmt, dass die maximal zulässige Hertzsche Pressung zwischen der Rollenoberfläche der Laufrolle und der Lauffläche des Nockens bei der gegebenen Belastung der Pumpenbaugruppe nicht überschritten wird. Die Wälzfestigkeit der Laufrolle und des Nockens ist dabei nicht definiert.By the GB 896 030 A For example, a high pressure pump is known having a pump assembly and a drive shaft having a cam associated with the pump assembly. The pump assembly has a roller having a roller surface, wherein the Roller is arranged on a running surface of the cam. The shape of the tread of the cam is determined so that the maximum allowable Hertzian pressure between the roller surface of the roller and the tread of the cam is not exceeded at the given load of the pump assembly. The rolling resistance of the roller and the cam is not defined.

Durch die US 2 735 313 A ist ein Rollenstößel bekannt, der für den Antrieb einer Einspritzpumpe verwendet werden kann. Der Rollenstößel weist eine Laufrolle auf, die eine Rollenoberfläche aufweist, wobei die Laufrolle an einer Lauffläche eines Nockens einer Antriebswelle angeordnet ist. Die Rollenoberfläche und die Lauffläche des Nockens sind ballig ausgebildet um bei einer Schrägstellung der Laufrolle zum Nocken ein Abrollen der Laufrolle auf der Lauffläche des Nockens sicherzustellen. Angaben zur Wälzfestigkeit der Laufrolle und des Nockens sind nicht vorhanden.By the US Pat. No. 2,735,313 a roller tappet is known which can be used to drive an injection pump. The roller tappet has a roller having a roller surface, wherein the roller is arranged on a running surface of a cam of a drive shaft. The roller surface and the tread of the cam are formed crowned to ensure an unrolling of the roller to the cam rolling the roller on the tread of the cam. Information on the rolling resistance of the roller and the cam are not available.

Offenbarung der ErfindungDisclosure of the invention

Die erfindungsgemäße Hochdruckpumpe mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass ein zuverlässiger Betrieb, insbesondere eine verbesserte Haltbarkeit des Nockens und/oder der Laufrolle, erzielt ist. Speziell sind der Nocken und die Laufrolle im Hinblick auf die im Betrieb auftretende schwellende Beanspruchung verbessert ausgestaltet.The high-pressure pump according to the invention with the features of claim 1 has the advantage that a reliable operation, in particular an improved durability of the cam and / or the roller, is achieved. Specifically, the cam and the roller are designed to be improved with respect to the swelling stress occurring during operation.

Durch die Ausbildung der Hochdruckpumpe gemäß Anspruch 1 kann bei unterschiedlichen Geometrien der Laufrolle und des Nockens die Ausprägung einer kritischen Schwellspannung für die Laufrolle und den Nocken im Betrieb gleich kritisch ausgelegt werden. Hierdurch ist eine Optimierung hinsichtlich einer Streckgrenze der Laufrolle und einer Streckgrenze des Nockens möglich. Im oberen Totpunkt ist die Hertzsche Pressung an der Rollenoberfläche der Laufrolle gleich groß wie die Hertzsche Pressung an der Lauffläche des Nockens. Die Hertzsche Pressung muss dabei jeweils kleiner sein als die Streckgrenze der Laufrolle beziehungsweise des Nockens. In vorteilhafter Weise kann durch die angepasste Ausgestaltung der Laufrolle an den Nocken die Ermüdung der beiden Bauteile Laufrolle und Nocken optimiert werden.Due to the design of the high-pressure pump according to claim 1, the expression of a critical threshold voltage for the roller and the cam during operation can be interpreted equally critical in different geometries of the roller and the cam. As a result, an optimization in terms of a yield strength of the roller and a yield point of the cam is possible. At top dead center, the Hertzian pressure on the roller surface of the roller is the same as the Hertzian pressure on the tread of the cam. The Hertzian pressure must in each case be smaller than the yield strength of the roller or of the cam. Advantageously, the fatigue of the two components roller and cam can be optimized by the adapted design of the roller on the cam.

Erfindungsgemäß ist es, dass der Radius der Laufrolle kleiner ist als der Krümmungsradius des Nockens an der Stelle der Lauffläche, an der die Laufrolle in einem oberen Totpunkt der Pumpenbaugruppe anliegt und dass die Laufrolle zumindest eine Bohrung aufweist, die sich zumindest teilweise in Richtung einer Drehachse der Laufrolle erstreckt. Hierbei ist es ferner vorteilhaft, dass die Bohrung bezüglich der Drehachse der Laufrolle zumindest im wesentlichen als axiale oder zumindest im Wesentlichen als koaxiale Bohrung ausgestaltet ist und/oder dass die Bohrung als Durchgangsbohrung ausgestaltet ist, die sich von einer Seite der Laufrolle zu einer anderen Seite der Laufrolle erstreckt. Hierdurch kann bei unterschiedlichen Geometrien im oberen Totpunkt eine Verringerung der Steifigkeit der Laufrolle im Bereich ihrer Rollenoberfläche erzielt werden.According to the invention, the radius of the roller is smaller than the radius of curvature of the cam at the location of the running surface on which the roller rests in a top dead center of the pump assembly and in that the roller has at least one bore extending at least partially in the direction of a rotation axis the roller extends. Here it is further advantageous that the bore with respect to the axis of rotation of the roller is at least substantially configured as an axial or at least substantially coaxial bore and / or that the bore is configured as a through hole extending from one side of the roller to another side of the roller. In this way, a reduction in the stiffness of the roller in the region of its roller surface can be achieved with different geometries at top dead center.

Vorteilhaft ist es auch, dass der Radius der Laufrolle kleiner ist als der Krümmungsradius des Nockens an der Stelle der Lauffläche, an der die Laufrolle in einem oberen Totpunkt der Pumpenbaugruppe anliegt, und dass zumindest eine Druckeigenspannung der Laufrolle an ihrer Rollenoberfläche erhöht ist. Speziell ist es vorteilhaft, dass die Rollenoberfläche der Laufrolle einsatzgehärtet und/oder kugelgestrahlt und/oder rolliert und/oder nitriert und/oder nitrocarburiert ist. Hierdurch kann bei unterschiedlichen Geometrien der Laufrolle und des Nockens am oberen Totpunkt die Wälzfestigkeit der Laufrolle durch Einbringen von Druckeigenspannung an der Oberfläche erhöht werden. Hierdurch ist eine vorteilhafte Anpassung der Laufrolle an den Nocken möglich.It is also advantageous that the radius of the roller is smaller than the radius of curvature of the cam at the location of the tread on which the roller rests in a top dead center of the pump assembly, and that at least one compressive residual stress of the roller is increased at its roller surface. Specifically, it is advantageous that the roller surface of the roller case hardened and / or shot peened and / or rolled and / or nitrided and / or nitrocarburized. In this way, the rolling resistance of the roller can be increased by introducing compressive residual stress at the surface at different geometries of the roller and the cam at top dead center. As a result, an advantageous adaptation of the roller to the cam is possible.

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 einen auszugsweisen Schnitt durch die in Fig. 1 dargestellte Hochdruckpumpe entlang der mit II bezeichneten Schnittlinie.
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 an excerpted section through the in Fig. 1 illustrated high-pressure pump along the designated II section line.

Fig. 1 zeigt eine Hochdruckpumpe 1 in einer schematischen, axialen Schnittdarstellung entsprechend einem ersten Ausführungsbeispiel der Erfindung. Die Hochdruckpumpe 1 kann insbesondere als Radial- oder Reihenkolbenpumpe für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Speziell eignet sich die Hochdruckpumpe 1 für eine Brennstoffeinspritzanlage mit einem 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 a first embodiment of the invention. The high-pressure pump 1 can serve in particular as a radial or series piston pump for fuel injection systems of air-compressing, self-igniting internal combustion engines. Specifically, the high-pressure pump 1 is suitable for a fuel injection system with a 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 Gehäuse 2 auf. In diesem Ausführungsbeispiel besteht das Gehäuse 2 aus den Gehäuseteilen 3, 4, 5, wobei das Gehäuseteil 3 einen Grundkörper, das Gehäuseteil 4 einen Zylinderkopf und das Gehäuseteil 5 einen an dem Grundkörper 3 befestigten Flansch darstellt.The high-pressure pump 1 has a multi-part housing 2. In this embodiment, the housing 2 consists of the housing parts 3, 4, 5, wherein the housing part 3 is a base body, the housing part 4 is a cylinder head and the housing part 5 is a fixed to the base body 3 flange.

Die Hochdruckpumpe 1 weist eine Antriebswelle 6 auf, die an Lagerstellen 7, 8 in den Gehäuseteilen 3, 5 gelagert ist. Zwischen den Lagerstellen 7, 8 weist die Antriebswelle 6 einen Nocken 9 auf. Der Nocken 9 ist in diesem Ausführungsbeispiel als Zweifachnocken ausgestaltet. Der Nocken 9 kann auch als Einfach- oder als ein anderer Mehrfachnocken ausgestaltet sein.The high-pressure pump 1 has a drive shaft 6 which is mounted at bearing points 7, 8 in the housing parts 3, 5. Between the bearings 7, 8, the drive shaft 6 has a cam 9. The cam 9 is designed in this embodiment as a double cam. The cam 9 can also be configured as a single or as another multiple cam.

Das Gehäuseteil 3 der Hochdruckpumpe 1 weist eine Führungsbohrung 12 auf, in der eine Pumpenbaugruppe 13 angeordnet ist. Der Nocken 9 ist der Pumpenbaugruppe 13 zugeordnet. Je nach Ausgestaltung der Hochdruckpumpe 1 können auch mehrere der Pumpenbaugruppe 13 entsprechende Pumpenbaugruppen vorgesehen sein. Solche Pumpenbaugruppen können dem Nocken 9 oder einem anderen Nocken, der dem Nocken 9 entspricht, zugeordnet sein. Hierdurch kann je nach Ausgestaltung eine Radial- oder Reihenkolbenpumpe verwirklicht werden.The housing part 3 of the high-pressure pump 1 has a guide bore 12, in which a pump assembly 13 is arranged. The cam 9 is associated with the pump assembly 13. Depending on the design of the high-pressure pump 1, a plurality of pump assemblies 13 may be provided corresponding pump assemblies. Such pump assemblies may be associated with the cam 9 or another cam corresponding to the cam 9. As a result, depending on the embodiment, a radial or piston pump can be realized.

Das als Zylinderkopf ausgestaltete Gehäuseteil 4 weist einen Ansatz 14 auf, der sich in die Führungsbohrung 12 erstreckt. Der Ansatz 14 weist eine Zylinderbohrung 15 auf, in der ein Kolben 16 in Richtung einer Achse 17 der Führungsbohrung 12 verschiebbar geführt ist, wie es durch einen Doppelpfeil 18 veranschaulicht ist. Der Kolben 16 begrenzt einen Pumpenarbeitsraum 19 in der Zylinderbohrung 15. Über ein an dem Gehäuseteil 4 vorgesehenes Einlassventil 20 ist Brennstoff aus einem Brennstoffkanal 21 in den Pumpenarbeitsraum 19 einleitbar. Ferner ist an dem Gehäuseteil 4 ein Auslassventil 22 vorgesehen, über das unter hohem Druck stehender Brennstoff aus dem Pumpenarbeitsraum 19 zu einem Brennstoffkanal 13 führbar ist. Der Brennstoffkanal 13 kann beispielsweise mit einem Common-Rail verbunden sein, um unter hohem Druck stehenden Brennstoff zu dem Common-Rail zu führen.The designed as a cylinder head housing part 4 has a projection 14 which extends into the guide bore 12. The projection 14 has a cylinder bore 15 in which a piston 16 is slidably guided in the direction of an axis 17 of the guide bore 12, as illustrated by a double arrow 18. The piston 16 defines a pump working space 19 in the cylinder bore 15. Via an inlet valve 20 provided on the housing part 4, fuel from a fuel passage 21 can be introduced into the pump working space 19. Furthermore, an outlet valve 22 is provided on the housing part 4, can be guided through the fuel under high pressure from the pump working chamber 19 to a fuel passage 13. The fuel channel 13 may, for example, be connected to a common rail in order to guide fuel under high pressure to the common rail.

Die Pumpenbaugruppe 13 weist eine Laufrolle 25 auf, die von einem Rollenschuh 26 aufgenommen ist. Der Rollenschuh 26 ist dabei in einem im Wesentlichen hohlzylinderförmigen Stößelkörper 27 eingesetzt. Ferner ist der Stößelkörper 27 mit einem scheibenförmigen Mitnahmeelement 28 verbunden, das den Kolben 16 oberhalb eines Bundes 29 des Kolbens 16 umgreift. Dadurch ist der Kolben 16 über seinen Bund 29 in Anlage mit dem Rollenschuh 26 gehalten. Ferner ist eine Kolbenfeder 30 vorgesehen, die auf den Stößelkörper 27 und/oder das Mitnahmeelement 28 einwirkt und somit den Stößelkörper 27 zusammen mit dem Kolben 16 in Richtung auf die Laufrolle 25 mit einer gewissen Federkraft beaufschlagt. Dadurch liegen der Kolben 16 mit seinem Bund 29, der Rollenschuh 26, die Rolle 25 und eine Lauffläche 10 des Nockens 9 jeweils aneinander an, wobei diese gegenseitige Anlage auch bei hohen Drehzahlen der Hochdruckpumpe 1 gewährleistet ist.The pump assembly 13 has a roller 25 which is received by a roller shoe 26. The roller shoe 26 is inserted in a substantially hollow cylindrical plunger body 27. Further, the plunger body 27 is connected to a disc-shaped driving element 28, which surrounds the piston 16 above a collar 29 of the piston 16. As a result, the piston 16 is held in contact with the roller shoe 26 via its collar 29. Further, a piston spring 30 is provided which on the plunger body 27 and / or the driving element 28 acts and thus acts on the plunger body 27 together with the piston 16 in the direction of the roller 25 with a certain spring force. As a result, the piston 16 with its collar 29, the roller shoe 26, the roller 25 and a running surface 10 of the cam 9 in each case against each other, this mutual contact is ensured even at high speeds of the high-pressure pump 1.

Im Betrieb der Hochdruckpumpe 1 wird dadurch die durch den Doppelpfeil 18 veranschaulichte Hin- und Herbewegung des Kolbens 16 erzielt, so dass die Förderung von unter hohem Druck stehenden Brennstoff zu dem Common-Rail erfolgt. Während eines Pumpenhubs des Kolbens 16 zum Fördern von Brennstoff zu dem Common-Rail über den Brennstoffkanal 23 wirkt eine relativ große Pumpenkraft F (Fig. 2) über den Rollenschuh 26 auf die Laufrolle 25. Die Laufrolle 25 stützt sich hierbei an der Lauffläche 10 ab.During operation of the high-pressure pump 1, the reciprocating movement of the piston 16 illustrated by the double arrow 18 is thereby achieved, so that the delivery of high-pressure fuel to the common rail takes place. During a pump stroke of the piston 16 for conveying fuel to the common rail via the fuel passage 23, a relatively large pumping force F (FIG. Fig. 2 ) on the roller shoe 26 on the roller 25. The roller 25 is supported here on the tread 10 from.

Im Betrieb der Hochdruckpumpe 1 rotiert die Antriebswelle 6 um eine Achse 31. Ferner läuft die Laufrolle 25 an der Lauffläche 10 des Nockens 9 ab. Eine Drehachse 32 der Laufrolle 25 ist hierbei zumindest näherungsweise parallel zu der Achse 31 der Antriebswelle 6 orientiert. Die Laufrolle 25 weist eine Rollenoberfläche 35 auf. Die Laufrolle 25 rollt mit ihrer Rollenoberfläche 35 im Betrieb an der Lauffläche 10 des Nockens 9 ab.During operation of the high pressure pump 1, the drive shaft 6 rotates about an axis 31. Further, the roller 25 runs on the running surface 10 of the cam 9 from. An axis of rotation 32 of the roller 25 is in this case oriented at least approximately parallel to the axis 31 of the drive shaft 6. The roller 25 has a roller surface 35. The roller 25 rolls with its roller surface 35 in operation on the running surface 10 of the cam 9 from.

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

Fig. 2 zeigt einen auszugsweisen Schnitt durch die in Fig. 1 dargestellte Hochdruckpumpe 1 entlang der mit II bezeichneten Schnittlinie. Hierbei zeigt die Fig. 2 eine Situation, in der ein oberer Totpunkt der Pumpenbaugruppe 13 erreicht ist. Die Laufrolle 25 liegt hierbei mit ihrer Rollenoberfläche 35 an einer Stelle 36 der Lauffläche 10 des Nockens 9 an. In dieser Stellung beziehungsweise im Bereich dieser Stellung tritt die höchste Beanspruchung der Laufrolle 25 sowie des Nockens 9 auf. Dabei wird der maximale Förderhub des Kolbens 16 der Pumpenbaugruppe 13 erreicht, so dass der maximale, von der Hochdruckpumpe 1 erzeugbare Druck im Pumpenarbeitsraum 19 besteht. Dies wirkt sich in einer entsprechend großen Kraft F aus. Fig. 2 shows an excerpted section through the in Fig. 1 illustrated high pressure pump 1 along the designated II cutting line. This shows the Fig. 2 a situation in which an upper dead center of the pump assembly 13 is reached. The roller 25 rests with its roller surface 35 at a point 36 of the tread 10 of the cam 9. In this position or in the region of this position, the highest stress of the roller 25 and the cam 9 occurs. In this case, the maximum delivery stroke of the piston 16 of the pump assembly 13 is reached, so that the maximum pressure which can be generated by the high-pressure pump 1 exists in the pump working chamber 19. This affects a correspondingly large force F.

Die Laufrolle 25 und der Nocken 9 können aus gehärteten hochfesten Werkzeugstählen hergestellt sein. Hierbei sind eine geometrische Ausgestaltung und ein Laufrollen-Werkstoff der Laufrolle 25 sowie eine geometrische Ausgestaltung des Nockens und ein Nocken-Werkstoff des Nockens 9 so gewählt, dass eine Wälzbeanspruchbarkeit der Laufrolle 25 und eine Wälzbeanspruchbarkeit des Nockens 9 an der Lauffläche 10 des Nockens 9 zumindest näherungsweise gleich groß vorgegeben sind. In diesem Ausführungsbeispiel ist speziell die Wälzbeanspruchbarkeit des Nockens 9 an der Stelle 36 seiner Lauffläche 10 relevant, da hier eine maximale Wälzbeanspruchung des Nockens 9 auftritt. Durch die Ausgestaltung des Nockens 9 als Zweifachnocken 9 tritt eine entsprechend große Wälzbeanspruchung auch an einer weiteren Stelle 37 der Lauffläche 10 des Nockens 9 auf. Die Stelle 37 ist dabei bezüglich der Achse 31 der Antriebswelle 6 gegenüberliegend zu der Stelle 36 an der Lauffläche 10 angeordnet.The roller 25 and the cam 9 may be made of hardened high strength tool steels. In this case, a geometric configuration and a roller material of the roller 25 and a geometric configuration of the cam and a cam material of the cam 9 are selected so that a Wälzbeanspruchbarkeit the roller 25 and a Wälzbeanspruchbarkeit of the cam 9 on the tread 10 of the cam 9 are at least approximately the same size. In this embodiment, especially the rolling load capacity of the cam 9 at the point 36 of its tread 10 is relevant, since a maximum rolling load of the cam 9 occurs here. Due to the design of the cam 9 as a double cam 9, a correspondingly large rolling stress also occurs at a further point 37 of the tread 10 of the cam 9. The point 37 is arranged with respect to the axis 31 of the drive shaft 6 opposite to the point 36 on the tread 10.

Die Laufrolle 35 ist zumindest näherungsweise zylinderförmig ausgestaltet. Die Laufrolle 25 weist bezüglich ihrer Rollenoberfläche 35 einen Radius 38 auf. Außerdem weist der Nocken 9 bezüglich seiner Lauffläche 10 einen umfänglich variierenden Krümmungsradius auf. Da die höchste Wälzbeanspruchung des Nockens 9 im Bereich der Stellen 36, 37 auftritt, ist ein Krümmungsradius 39 an der Stelle 36 relevant, an der die Laufrolle 25 in dem oberen Totpunkt der Pumpenbaugruppe 13 an der Lauffläche 10 anliegt. Für die Stelle 37 ergibt sich hierbei ein entsprechender Krümmungsradius 40, der gleich dem Krümmungsradius 39 ist.The roller 35 is designed at least approximately cylindrical. The roller 25 has a radius 38 with respect to its roller surface 35. In addition, the cam 9 with respect to its tread 10 has a circumferentially varying radius of curvature. Since the highest rolling load of the cam 9 in the areas of the points 36, 37 occurs, a radius of curvature 39 at the point 36 is relevant, where the roller 25 abuts the tread 10 at the top dead center of the pump assembly 13. For the location 37, this results in a corresponding radius of curvature 40, which is equal to the radius of curvature 39.

Je nach Ausgestaltung der Hochdruckpumpe 1 kann der Radius 38 der Laufrolle 25 kleiner oder auch größer als der Krümmungsradius 39 des Nockens 9 sein.Depending on the configuration of the high pressure pump 1, the radius 38 of the roller 25 may be smaller or larger than the radius of curvature 39 of the cam 9.

In der in der Fig. 1 dargestellten Stellung des Nockens 9 im oberen Totpunkt der Pumpenbaugruppe 13 ist die Hertzsche Pressung an der Lauffläche 10 des Nockens 9 sowie der Rollenoberfläche 35 der Laufrolle 25 für beide Bauteile 9, 25 gleich groß. Diese Hertzsche Pressung muss für einen zuverlässigen Betrieb kleiner sein als die Streckgrenze der Bauteile Laufrolle 25 und Nocken 9. Da die Beanspruchung im Betrieb hochdynamisch erfolgt, ist im Hinblick auf einen zuverlässigen Betrieb eine Ermüdung der Laufrolle 25 und/oder eine Ermüdung des Nockens 9 von Bedeutung. Die schwellende Beanspruchung der Laufrolle 25 und des Nockens 9 hat ihr Maximum unterhalb der Rollenoberfläche 35 beziehungsweise der Lauffläche 10. Ferner ist die schwellende Belastung abhängig von der Beanspruchung, der Geometrie, insbesondere dem Radius 38 der Laufrolle 25 und den Krümmungsradien 39, 40 an den Stellen 36, 37, und des Elastizitätsmoduls der Laufrolle 25 beziehungsweise des Nockens 9. Für einen zuverlässigen Betrieb über die Lebensdauer der Hochdruckpumpe 1 darf die schwellende Beanspruchung die zulässige Wälzfestigkeit des für die Bauteile 25, 9 verwendeten Werkstoffs beziehungsweise der Werkstoffe nicht überschreiten. Die schwellende Beanspruchung wirkt sich dabei um so stärker aus, je kleiner der Radius 38 der Laufrolle 25 beziehungsweise der Krümmungsradius 39 des Nockens 9 ist. Somit wird das Bauteil 25, 29 stärker belastet, das den kleineren Radius 38 beziehungsweise Krümmungsradius 39 aufweist.In the in the Fig. 1 illustrated position of the cam 9 at top dead center of the pump assembly 13 is the Hertzian pressure on the tread 10 of the cam 9 and the roller surface 35 of the roller 25 for both components 9, 25 the same size. This Hertzian pressure must be less than the yield strength of the components roller 25 and cam 9 for reliable operation. Since the stress in operation is highly dynamic, fatigue of the roller 25 and / or fatigue of the cam 9 is due to reliable operation Meaning. The swelling stress of the roller 25 and the cam 9 has its maximum below the roller surface 35 and the tread 10. Furthermore, the swelling load depending on the stress, the geometry, in particular the radius 38 of the roller 25 and the radii of curvature 39, 40 to the For a reliable operation over the life of the high-pressure pump 1, the swelling stress must not exceed the permissible rolling strength of the material used for the components 25, 9 or the materials. The swelling stress has an even greater effect, the smaller the radius 38 of the roller 25 or the radius of curvature 39 of the cam 9. Thus, the component becomes 25, 29 more heavily loaded, which has the smaller radius 38 or radius of curvature 39.

In vorteilhafter Weise wird die kritische Schwellspannung für beide Bauteile 9, 25 gleich kritisch im Hinblick auf die zulässige Wälzbeanspruchung ausgelegt. Beispiele für mögliche Auslegungen sind im Folgenden weiter beschrieben.Advantageously, the critical threshold voltage for both components 9, 25 is designed to be equally critical with regard to the permissible rolling load. Examples of possible interpretations are described further below.

Falls der Radius 38 der Laufrolle 25 kleiner vorgegeben ist als der Krümmungsradius 39 des Nockens 9, dann ist ein Elastizitätsmodul des Laufrollen-Werkstoffs, aus dem die Laufrolle 25 zumindest im Bereich ihrer Rollenoberfläche 35 gebildet ist, kleiner als ein Elastizitätsmodul des Nocken-Werkstoffs, aus dem der Nocken 9 zumindest im Bereich seiner Lauffläche 10 gebildet ist. Möglich ist es in diesem Fall auch, dass die Laufrolle zumindest eine Bohrung 41 aufweist. Solch eine Bohrung 41 ermöglicht eine Verringerung der Steifigkeit der Laufrolle 25, insbesondere im Bereich ihrer Rollenoberfläche 35. Die Bohrung 41 ist vorzugsweise als axiale oder koaxiale Bohrung 41 ausgestaltet. In diesem Ausführungsbeispiel ist die Bohrung 41 als axiale Bohrung ausgestaltet, die sich entlang der Drehachse 32 der Laufrolle 25 erstreckt. Die Bohrung 41 ist in diesem Ausführungsbeispiel als Durchgangsbohrung 41 ausgestaltet. Die Bohrung 41 erstreckt sich von einer Seite 42 der Laufrolle 25 bis zu einer anderen Seite 43 der Laufrolle 25, die von der Seite 42 abgewandt ist.If the radius 38 of the roller 25 is set smaller than the radius of curvature 39 of the cam 9, then a modulus of elasticity of the roller material, from which the roller 25 is formed at least in the region of its roller surface 35, is smaller than a modulus of elasticity of the cam material, from which the cam 9 is formed at least in the region of its tread 10. It is also possible in this case that the roller has at least one bore 41. Such a bore 41 allows a reduction in the rigidity of the roller 25, in particular in the region of its roller surface 35. The bore 41 is preferably designed as an axial or coaxial bore 41. In this embodiment, the bore 41 is configured as an axial bore which extends along the axis of rotation 32 of the roller 25. The bore 41 is configured as a through hole 41 in this embodiment. The bore 41 extends from one side 42 of the roller 25 to another side 43 of the roller 25, which faces away from the side 42.

In dem Fall, in dem der Radius 38 der Laufrolle 25 kleiner ist als der Krümmungsradius 39 des Nockens 9 an der Stelle 36 der Lauffläche 10, ist es auch von Vorteil, dass Druckeigenspannungen der Laufrolle 25 an ihrer Rollenoberfläche 35 erhöht sind. Hierbei kann die Laufrolle 25 im Bereich ihrer Rollenoberfläche 35 bearbeitet sein. Speziell ist ein Einsatzhärten der Rollenoberfläche 35, ein Kugelstrahlen der Rollenoberfläche 35, ein Rollieren der Rollenoberfläche 35, ein Nitrieren der Rollenoberfläche 35 oder auch ein Nitrocarburieren der Rollenoberfläche 35 möglich. Hierdurch kann die Wälzfestigkeit der Laufrolle 25, insbesondere der Rollenoberfläche 35 der Laufrolle 25, durch Einbringen von Druckeigenspannungen an der Rollenoberfläche 35 erhöht werden.In the case where the radius 38 of the roller 25 is smaller than the radius of curvature 39 of the cam 9 at the location 36 of the tread 10, it is also advantageous that compressive residual stresses of the roller 25 on its roller surface 35 are increased. In this case, the roller 25 can be processed in the region of its roller surface 35. Specifically, case hardening of the roller surface 35, shot peening of the roller surface 35, rolling of the roller surface 35, nitriding of the roller surface 35 or even nitrocarburizing of the roller surface 35 are possible. In this way, the rolling resistance of the roller 25, in particular the roller surface 35 of the roller 25, can be increased by introducing compressive residual stresses on the roller surface 35.

In einem Fall, in dem der Radius 38 der Laufrolle 25 größer ist als der Krümmungsradius 39 des Nockens 9, ist der Elastizitätsmodul des Laufrollen-Werkstoffs, aus dem die Laufrolle 25 gebildet ist, größer als der Elastizitätsmodul des Nocken-Werkstoffs, aus dem der Nocken 9 zumindest an seiner Lauffläche 10 gebildet ist. Hierdurch ist ein Belastungsausgleich möglich, um die gleiche oder zumindest eine vergleichbare Belastung sowohl für die Laufrolle 25 als auch für den Nocken 9 zu erzielen. Möglich ist auch eine Bearbeitung, insbesondere eine Oberflächenbearbeitung, des Nockens 9. Diese kann entsprechend einer Oberflächenbearbeitung der Rollenoberfläche 35 der Laufrolle 25 ausgeführt sein.In a case where the radius 38 of the pulley 25 is larger than the radius of curvature 39 of the cam 9, the modulus of elasticity of the pulley material constituting the pulley 25 is greater than the modulus of elasticity of the cam material from which the pulley 25 Cam 9 is formed at least on its tread 10. As a result, a load compensation is possible to achieve the same or at least a comparable load for both the roller 25 and the cam 9. It is also possible to edit, especially one Surface treatment of the cam 9. This may be carried out according to a surface treatment of the roller surface 35 of the roller 25.

Claims (6)

  1. High-pressure pump (1), in particular a radial or inline piston pump for fuel injection systems of air-compressing autoignition internal combustion engines, with at least one pump subassembly (13) and with a driveshaft (6) which has at least one cam (9) assigned to the pump subassembly (13), the pump subassembly (13) having a running roller (25) which has a roller surface (35), and the running roller (25) being arranged on a running surface (10) of the cam (9), characterized in that a rolling resistance of the running roller (25) on the roller surface (35) of the running roller (25) and a rolling resistance of the cam (9) on the running surface (10) of the cam (9) are stipulated to be at least approximately equal, in that a radius (38) of the running roller (25) is smaller than a radius of curvature (39) of the cam (9) at a point (36) on the running surface (10) at which the running roller (25) comes to bear at top dead center of the pump subassembly (13), and a modulus of elasticity of a running roller material, from which the running roller (25) is formed at least on its roller surface (35), is lower than a modulus of elasticity of a cam material, from which the cam (9) is formed at least on its running surface (10), or in that a radius (38) of the running roller (25) is larger than a radius of curvature (39) of the cam (9) at a point (36) on the running surface (10) at which the running roller (25) comes to bear at top dead center of the pump subassembly (13), and a modulus of elasticity of a running roller material, from which the running roller (25) is formed at least on its roller surface (35), is higher than a modulus of elasticity of a cam material, from which the cam (9) is formed at least on its running surface (10) .
  2. High-pressure pump according to Claim 1, characterized in that a radius (38) of the running roller (25) is smaller than a radius of curvature (39) of the cam (9) at a point (36) on the running surface (10) at which the running roller (25) comes to bear at top dead center of the pump subassembly (13), and in that the running roller (25) has at least one bore (41) which extends at least partially in the direction of an axis of rotation (32) of the running roller (25).
  3. High-pressure pump according to Claim 2, characterized in that the bore (41) is configured at least essentially as an axial or at least essentially as a coaxial bore (41) with respect to the axis of rotation (32) of the running roller (25), and/or in that the bore (41) is configured as a through bore (41) which extends from one side (42) of the running roller (25) to another side (43) of the running roller (25).
  4. High-pressure pump according to one of Claims 1 to 3, characterized in that at least one characteristic compressive stress of the running roller (25) on its roller surface (35) is increased.
  5. High-pressure pump according to Claim 4, characterized in that the roller surface (35) of the running roller (25) is case-hardened and/or shot-peened and/or tumbled and/or nitrided and/or carbonitrided.
  6. High-pressure pump according to one of Claims 1 to 5, characterized in that at least one characteristic compressive stress of the cam (9) on its running surface (10) is increased.
EP10709736.2A 2009-05-13 2010-03-22 High pressure pump Active EP2430303B1 (en)

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DE102009003054A DE102009003054A1 (en) 2009-05-13 2009-05-13 high pressure pump
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JP (1) JP5491621B2 (en)
KR (1) KR101682737B1 (en)
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Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011082642A1 (en) 2011-09-14 2013-03-14 Robert Bosch Gmbh Pump, in particular high-pressure fuel pump for a fuel injection device of an internal combustion engine
US20130192564A1 (en) * 2012-01-26 2013-08-01 Cummins Inc. Laser shock peening applied to fuel system pump head
JP5812020B2 (en) * 2013-02-07 2015-11-11 株式会社デンソー Fuel supply pump
DE102013204327A1 (en) * 2013-03-13 2014-09-18 Robert Bosch Gmbh Cylinder head blank, cylinder head and high-pressure pump for fuel injection systems
DE102013206902A1 (en) * 2013-04-17 2014-10-23 Robert Bosch Gmbh high pressure pump
DE102013212146A1 (en) 2013-06-25 2015-01-08 Robert Bosch Gmbh pump
DE102013212145A1 (en) 2013-06-25 2015-01-08 Robert Bosch Gmbh pump
DE102013212304A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
DE102013212302A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh High pressure pump and fuel injection system with a high pressure pump
DE102013212261A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
DE102013212248A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh high pressure pump
FR3015598B1 (en) * 2013-12-23 2016-12-23 Skf Ab FOLLOWING ROLL DEVICE OF A CAM
DE102014204312A1 (en) 2014-03-10 2015-09-10 Robert Bosch Gmbh high pressure pump
DE102014205260A1 (en) 2014-03-20 2015-09-24 Robert Bosch Gmbh high pressure pump
DE102014206968A1 (en) 2014-04-10 2015-10-15 Robert Bosch Gmbh High pressure pump and high pressure directional valve
DE102014219293A1 (en) 2014-09-24 2016-03-24 Robert Bosch Gmbh Pump, in particular high-pressure pump for fuel injection systems, with a sealing device
DE102014219611A1 (en) 2014-09-26 2016-03-31 Robert Bosch Gmbh Camshaft and pump with a camshaft
DE102014223597B4 (en) * 2014-10-08 2019-02-07 Continental Automotive Gmbh Roller for a roller tappet of a high-pressure fuel pump, roller tappet, high-pressure fuel pump and internal combustion engine
US9835123B2 (en) 2015-01-13 2017-12-05 Roller Bearing Company Of America, Inc. Roller for a fuel pump actuator
CN104879255B (en) * 2015-04-13 2017-12-22 广州柴油机厂股份有限公司 A kind of G26 diesel oil model machine injection advance angle adjustment instrument and application method
DE102018211237A1 (en) * 2018-07-07 2020-01-09 Robert Bosch Gmbh Fuel pump

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2735313A (en) * 1956-02-21 Dickson

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3034363A (en) * 1958-12-13 1962-05-15 Bosch Gmbh Robert Cam drive
GB896030A (en) * 1958-12-13 1962-05-09 Bosch Gmbh Robert Improvements in or relating to cams
US3451277A (en) * 1967-06-19 1969-06-24 Whitin Machine Works Cam mechanism
GB1252001A (en) * 1968-02-12 1971-11-03
US4104956A (en) * 1969-06-10 1978-08-08 Hitachi Construction Machinery Co., Ltd. Radial piston type multi-stroke hydraulic pump or motor
US4099597A (en) * 1976-08-23 1978-07-11 Houdaille Industries, Inc. Lubrication pump
JPS61146462A (en) * 1984-12-19 1986-07-04 Toyoda Mach Works Ltd Cam shaft grinding attachment
DE3779486D1 (en) * 1986-04-21 1992-07-09 Bosch Robert CAMSHAFT.
US5215449A (en) * 1991-12-05 1993-06-01 Stanadyne Automotive Corp. Distributor type fuel injection pump
JPH05231260A (en) * 1992-02-18 1993-09-07 Nippondenso Co Ltd Distribution type fuel injection pump
JP3618977B2 (en) * 1997-11-05 2005-02-09 光洋精工株式会社 Cam tappet device
JP2001263198A (en) * 2000-03-14 2001-09-26 Bosch Automotive Systems Corp Fuel pump and fuel supply device using it
JP2002115623A (en) * 2000-10-05 2002-04-19 Mitsubishi Electric Corp Variable discharge-amount fuel supply device
JP2003056315A (en) * 2001-08-22 2003-02-26 Ntn Corp Roller-equipped cam follower
CN2627233Y (en) * 2003-05-21 2004-07-21 上海东维燃油喷射有限公司 Tappet unit with locating slot and without ferrule
KR100738778B1 (en) * 2004-01-14 2007-07-12 봇슈 가부시키가이샤 Fuel supply pump and tappet structure body
US20060005797A1 (en) * 2004-07-08 2006-01-12 Schubeck Joseph J Roller valve lifter
DE102005046670A1 (en) 2005-09-29 2007-04-05 Robert Bosch Gmbh High pressure pump for fuel injection device of internal combustion engine, has ball indirectly fixed in part of base plate in tangential direction to tappet and engaged in groove approximately radial to longitudinal axis of tappet
DE102005059031A1 (en) * 2005-12-10 2007-06-14 Schaeffler Kg Radial piston high pressure pump e.g. radial piston distributor type fuel injection pump, for internal combustion engine, has thrust surface of cam ring, guidance slot surface, rolling pickers surface and rolls surface, with micro recesses
DE102006041673A1 (en) * 2006-02-20 2007-08-23 Robert Bosch Gmbh High pressure pump especially for fuel injection in IC engine has the cam follower supported axially by hardened low wear surfaces
JP2007315342A (en) * 2006-05-29 2007-12-06 Nissan Motor Co Ltd Pressure fluctuation restricting means and fuel supply system equipped therewith
US7748359B2 (en) * 2006-06-30 2010-07-06 Caterpillar Inc. Tappet assembly

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2735313A (en) * 1956-02-21 Dickson

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KR20120018316A (en) 2012-03-02
RU2011150403A (en) 2013-06-27
KR101682737B1 (en) 2016-12-05
JP2012526242A (en) 2012-10-25
US20120051951A1 (en) 2012-03-01
CN102422011A (en) 2012-04-18
RU2554377C2 (en) 2015-06-27
JP5491621B2 (en) 2014-05-14
DE102009003054A1 (en) 2010-11-18
WO2010130497A1 (en) 2010-11-18
CN102422011B (en) 2017-12-08

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