EP2430303B1 - High pressure pump - Google Patents
High pressure pump Download PDFInfo
- 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
- Authority
- EP
- European Patent Office
- Prior art keywords
- roller
- cam
- running
- running roller
- radius
- 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.)
- Active
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- 239000000446 fuel Substances 0.000 claims description 15
- 238000005096 rolling process Methods 0.000 claims description 14
- 239000000463 material Substances 0.000 claims description 13
- 238000002347 injection Methods 0.000 claims description 5
- 239000007924 injection Substances 0.000 claims description 5
- 238000002485 combustion reaction Methods 0.000 claims description 4
- 230000008961 swelling Effects 0.000 description 6
- 230000000712 assembly Effects 0.000 description 3
- 238000000429 assembly Methods 0.000 description 3
- 238000004381 surface treatment Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005121 nitriding Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000005480 shot peening Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Images
Classifications
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- 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
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- 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
- F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
- F02M41/08—Fuel-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
- F02M41/10—Fuel-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
- F02M41/12—Fuel-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
- F02M41/123—Fuel-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
- F02M41/128—Varying injection timing by angular adjustment of the face-cam or the rollers support
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- 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
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-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
- F02M45/04—Fuel-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
- F02M45/06—Pumps peculiar thereto
- F02M45/063—Delivery stroke of piston being divided into two or more parts, e.g. by using specially shaped cams
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- 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
- F02M59/445—Selection of particular materials
-
- 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
- F02M63/00—Other 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
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- 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/02—Fuel-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.
Landscapes
- 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
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
Die aus der
Durch die
Durch die
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
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
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 inFig. 1 dargestellte Hochdruckpumpe entlang der mit II bezeichneten Schnittlinie.
-
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 inFig. 1 illustrated high-pressure pump along the designated II section line.
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-
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-
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-
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
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
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 (
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
Die Hochdruckpumpe 1 des Ausführungsbeispiels ist im Folgenden auch unter Bezugnahme auf die
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
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
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
In der in der
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
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
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
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
Claims (6)
- 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) .
- 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).
- 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).
- 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.
- 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.
- 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.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009003054A DE102009003054A1 (en) | 2009-05-13 | 2009-05-13 | high pressure pump |
PCT/EP2010/053696 WO2010130497A1 (en) | 2009-05-13 | 2010-03-22 | High pressure pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2430303A1 EP2430303A1 (en) | 2012-03-21 |
EP2430303B1 true EP2430303B1 (en) | 2019-06-05 |
Family
ID=42244773
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10709736.2A Active EP2430303B1 (en) | 2009-05-13 | 2010-03-22 | High pressure pump |
Country Status (8)
Country | Link |
---|---|
US (1) | US20120051951A1 (en) |
EP (1) | EP2430303B1 (en) |
JP (1) | JP5491621B2 (en) |
KR (1) | KR101682737B1 (en) |
CN (1) | CN102422011B (en) |
DE (1) | DE102009003054A1 (en) |
RU (1) | RU2554377C2 (en) |
WO (1) | WO2010130497A1 (en) |
Families Citing this family (21)
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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 |
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- 2009-05-13 DE DE102009003054A patent/DE102009003054A1/en not_active Withdrawn
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- 2010-03-22 KR KR1020117026859A patent/KR101682737B1/en active IP Right Grant
- 2010-03-22 WO PCT/EP2010/053696 patent/WO2010130497A1/en active Application Filing
- 2010-03-22 EP EP10709736.2A patent/EP2430303B1/en active Active
- 2010-03-22 US US13/265,567 patent/US20120051951A1/en not_active Abandoned
- 2010-03-22 RU RU2011150403/06A patent/RU2554377C2/en active
- 2010-03-22 CN CN201080021222.1A patent/CN102422011B/en active Active
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Also Published As
Publication number | Publication date |
---|---|
EP2430303A1 (en) | 2012-03-21 |
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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