EP2464853B1 - High pressure pump - Google Patents
High pressure pump Download PDFInfo
- Publication number
- EP2464853B1 EP2464853B1 EP10728173.5A EP10728173A EP2464853B1 EP 2464853 B1 EP2464853 B1 EP 2464853B1 EP 10728173 A EP10728173 A EP 10728173A EP 2464853 B1 EP2464853 B1 EP 2464853B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- roller
- central bore
- pressure pump
- cam
- pump according
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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- 230000033001 locomotion Effects 0.000 claims description 6
- 230000007423 decrease Effects 0.000 claims description 4
- 238000002485 combustion reaction Methods 0.000 claims description 3
- 239000000446 fuel Substances 0.000 claims description 3
- 238000002347 injection Methods 0.000 claims description 3
- 239000007924 injection Substances 0.000 claims description 3
- 230000002093 peripheral effect Effects 0.000 description 8
- 230000007704 transition Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000009933 burial Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 239000000463 material 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
- F02M59/44—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
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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
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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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
Definitions
- the invention relates to a high-pressure pump for a fuel injection device of an internal combustion engine having the features of the preamble of claim 1.
- a high-pressure pump is for example from the published patent application DE 10 2006 041 673 A1 out.
- the high-pressure pump described herein comprises a drive shaft having at least one cam or eccentric and at least one pump element comprising a pump piston which is driven in a reciprocating motion by the cam or eccentric of the drive shaft.
- the pump piston is supported via a support member and a rotatably mounted in this support roller on the cam or eccentric of the drive shaft.
- Support member and roller are taken together in a bucket tappet for support, wherein contact areas between the roller and the bucket tappet and / or the support member are formed. Due to the rotational movement of the roller, these contact areas are subject to increased wear, so that it is proposed in the aforementioned document to provide the respective contact areas with a surface having a high Veschlberichtbericht.
- a radial piston displacement machine with hydrostatic torque transmission by means of roller piston is known in which the roller has a hollow cylindrical bore.
- the bore is filled with a pressure medium, so that it is possible to dispense with a self-supporting thickness of the roller due to the internal pressure.
- the internal pressure thus ensures a sufficient dimensional stability of the roller and at the same time allows an increased local nestling of the roller in a contact area with a cam disc. As a result, a reduced Hertzian pressure and increased compressive strength is achieved.
- the invention is based on the object to improve a high pressure pump of the type mentioned in terms of their wear resistance.
- the wear in the contact area of a roller with a cam or an eccentric of a drive shaft and / or with a roller receiving support element is to be reduced.
- the proposed high-pressure pump has at least one pump element which has a pump piston which can be driven in a reciprocating motion via a cam or eccentric of a drive shaft, the pump piston being indirectly supported via a plunger and a roller on the cam or eccentric of the drive shaft.
- the roller has at least one central bore which extends along the longitudinal axis A of the roller and has at least one conical, partially spherical and / or partially elliptical partial section for forming an inner contour which runs obliquely to the longitudinal axis A at least in a partial region.
- Such a running roller for supporting a pump piston on a cam or eccentric of the drive shaft has the advantage that over the inner contour of the at least one central bore, the rigidity of the roller can be adjusted.
- the roll has a less rigidity than in the sections which do not have a central bore.
- the central bore can also extend through the entire roller body, wherein an inner contour of the bore can be determined by juxtaposing conical, partially spherical and / or partially ellipsoidal sections, which leads to an optimization of the roller stiffness.
- the roller stiffness must be high enough to support the pump piston against the cam or eccentric, on the other hand, it should be so low that errors are compensated without fatigue.
- the weight of the roller can be significantly reduced by a central bore, this is especially true when the central bore extends through the entire roller body.
- a low weight and optimized roller stiffness lead to an improved contact pressure of the roller on the cam or eccentric, so that the dynamic load in the contact area of the roller with the cam or eccentric fails lower. Consequently, less wear occurs in this contact area.
- the high-pressure pump according to the invention is therefore characterized by a long service life.
- the at least one central bore is a blind hole extending inwardly from an end face of the roller.
- the two blind holes are preferably formed mirror-symmetrically with respect to a perpendicular bisector to the longitudinal axis A, that is, that they extend over an equally long axial portion a and have an inner contour which is mirrored.
- the two blind holes may be formed, for example, cone-shaped, part-spherical and / or jerllipsoid.
- the mirrored design of the two blind holes also contributes to a smooth running of the role on the cam or eccentric and is therefore to be preferred.
- the extent of the axial extent of the two blind holes is selected according to the requirements.
- the two end face side loosened blind holes cause the role in the region of its two end faces has a lower rigidity, so that the contact pressure of the roller is reduced in this area and the tread on the cam or eccentric due to less load has less tracks. This also leads to the edge area of the roll edge pressure is reduced, so that the role is exposed to less wear.
- the two blind bores or one central bore are formed such that the diameter from the inside to the outside, i. towards at least one end face, becomes larger.
- the rigidity of the roller decreases towards an end face. This not only has a favorable effect on the edge pressure on the roller, but also simplifies the production of such a roller.
- the central bore has no undercuts.
- the central bore can thus be set from the outside, from an end face.
- the at least one central bore can also be produced in one working step together with the roller, for example using a closed mold, since demolding is unproblematic due to the lack of undercuts.
- other manufacturing methods are possible.
- the central bore is rotationally symmetrical with respect to the longitudinal axis A of the roller.
- the roller in the cross section in the area of the central bore has circumferentially equal wall thicknesses. This ensures that the roller runs smoothly on the cam or on the eccentric of the drive shaft. The shape stiffness of the roll thus changes only along its axial extent.
- the central bore of the roller can also have a cylindrical section b.
- the roller has a constant stiffness, so that this section preferably forms a central portion of the roll.
- a cylindrical portion b may have a continuous central bore extending from one end face of the roll to the other.
- the cylindrical section b preferably has a smaller diameter than a subsequent section a. In this way, it is ensured that the inner contour has no undercuts.
- a cylindric portion is thus particularly easy to manufacture.
- the end faces of the roller are convexly curved and / or tapered at least over a partial region. If an end face has a central bore, the at least partially convexly curved and / or conically extending end face has a central recess. The end face may be rounded in the transition to the central bore. If the roller has a central bore on both end faces, only the remaining edge regions of the end faces that surround the respective bore form contact regions between the roller and the tappet.
- the roller is at least partially received in the plunger, wherein preferably the plunger is formed in the region of the roller receiving hollow cylindrical, so that the end faces of the roller at least partially abut an inner peripheral surface of the plunger.
- a roller shoe can also be arranged in the tappet. Since the roller shoe also experiences a dynamic load in the area of contact with the roller, the above-mentioned advantages also come into play in the contact area of the roller with the roller shoe.
- FIG.1 Partially illustrated pump element of a high-pressure pump according to the invention has a pump piston 1 which indirectly via a roller 4 on a cam 2 a drive shaft (not shown) supported is.
- the roller 4 is at least partially received in a plunger 3, which has a cup-shaped end.
- a roller shoe 9 is further provided, which is arranged between the plunger 3 and the roller 4.
- the rotation of the drive shaft is transmitted via the cam 2 to the roller 4, which rolls on the outer peripheral side on the cam 2.
- the outer peripheral side of the cam 2 thus forms a running surface 8.
- the contact areas of the roller 4 on the plunger 3 and on the tread 8 of the cam 2 are dynamically loaded. These contact areas are therefore subject to increased wear. These contact areas include on the one hand the end faces 6 and 6 ', which abut against the inner peripheral surface 7 of the cup-shaped end of the plunger 3. In the region of the adjacent end faces 6 and 6 ', therefore, the inner peripheral surface 7 of the plunger 3 is subjected to high stress.
- the outer peripheral surface 10 of the roller 4 forms a contact area with the running surface 8 of the cam 2.
- the roller 4 is hollow by having a central bore 5 extending from one end 6 to the other end 6 'along the longitudinal axis A of the roller 4 extends.
- the bore 5 has various sections, the sections a conical and the section b are cylindrical.
- the central bore 5 thus has a profiled inner contour, which allows optimization of the roller stiffness.
- the cylindrical portion b of the central bore 5 is arranged centrally. On both sides of the section b is followed in each case by a partial section a, which runs conically, wherein the diameter of the central bore 5 increases from the inside to the outside, to the side surfaces 6 and 6 '.
- the substantially hollow cylindrical roller 4 thus has a smaller thickness in the area of the side surfaces 6 and 6 '.
- the roller stiffness also decreases, so that it is the lowest in the area of the side surfaces 6 and 6 '. Accordingly, the roller stiffness can be adjusted via the inner contour of the central bore 5 such that the contact pressure of the roller 4 on the running surface 8 of the cam 2 in the region of the partial section a is less than in the region of the partial section b.
- the inner contour of which is composed of a first conically extending portion a, a cylindrical portion b and a second conical portion a is selected only by way of example.
- the inner contour of the central bore 5 can also zsuammenTER of two or more than three sections, which may also be formed partly spherical or teililipsoid beyond.
- the transitions of the sections may be flattened or rounded. The same applies to the transition of the central bore 5 in one of the end faces 6 and 6 '. These too can be flattened or rounded.
- the central bore 5 In order to allow a smooth running of the roller 4 on the tread 8 of the cam 2, the central bore 5 - regardless of the selected inner contour - rotationally symmetrical with respect to the longitudinal axis A. That is, in the cross section, the roller 4 in the region of the central bore 5 circumferentially has the same wall thickness. A uniform drainage is also ensured by the fact that the central bore 5 is designed mirror-symmetrically with respect to a central axis perpendicular to the longitudinal axis A.
- FIG. 2 An alterantive embodiment of the roller 4 of a pump element of a further high-pressure pump according to the invention is shown in FIG FIG. 2 shown.
- this roller 4 instead of a continuous central bore 5, this roller 4 on two blind holes 5, each extending from an end face 6 and 6 'inwards. These are also rotationally symmetrical with respect to the longitudinal axis A angordnet and have a mirrored inner contour.
- the illustrated embodiment shows two blind holes with eilipsenförmig extending inner contour. The transition of the holes 5 in the end faces 6 and 6 'is executed in each case rounded.
- the blind holes 5 on the end faces 6 and 6 'of the roller 4 cause them to have a lower rigidity in the sections a.
- the roller stiffness can also be optimized by forming two blind holes.
- the roller stiffness is determined by the respective inner contour of the holes 5, ie in particular over the length and the respective diameter ratios. Wear on the outer peripheral surface 10 of the roller 4 and the tread 8 of the cam 2
- each pump element has a roller 4 with at least one central bore 5, which has an inner contour that determines the roller stiffness.
- the roll material is preferably also taken into account.
- a wear-reducing effect has the proposed role training also in relation to a possibly provided roller shoe 9, on which the roller 4 can be additionally supported.
- a roller shoe 9 need not necessarily be provided.
- the roller 4 may also be supported via other support elements in addition to the plunger 3.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Description
Die Erfindung betrifft eine Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung einer Brennkraftmaschine mit den Merkmalen des Oberbegriffs des Anspruchs 1. Eine solche Hochdruckpumpe geht beispielsweise aus der Offenlegungsschrift
Nicht nur der Kontaktbereich zwischen der Rolle und der Rollenaufnahme wird im Betrieb der Pumpe einer dynamischen Belastung unterzogen, sondern auch der Kontaktbereich zwischen Rolle und Nocken bzw. Exzenter der Antriebswelle. Auch dieser Kontaktbereich unterliegt daher einem erhöhten Verschleiß. Insbesondere kann es zum Eingraben der Rolle in die Lauffläche am Nocken bzw. Exzenter kommen.Not only the contact area between the roller and the roller receiving a dynamic load is subjected during operation of the pump, but also the contact area between the roller and the cam or eccentric of the drive shaft. This contact area is therefore subject to increased wear. In particular, it may come to the burial of the role in the tread on the cam or eccentric.
Aus der
Ausgehend vom bekannten Stand der Technik liegt der Erfindung die Aufgabe zu Grunde, eine Hochdruckpumpe der eingangs genannten Art im Hinblick auf ihre Verschleißfestigkeit zu verbessern. Insbesondere soll der Verschleiß im Kontaktbereich einer Rolle mit einem Nocken oder einem Exzenter einer Antriebswelle und/oder mit einem die Rolle aufnehmenden Stützelement verringert werden.Based on the known prior art, the invention is based on the object to improve a high pressure pump of the type mentioned in terms of their wear resistance. In particular, the wear in the contact area of a roller with a cam or an eccentric of a drive shaft and / or with a roller receiving support element is to be reduced.
Zur Lösung dieser Aufgabe wird eine Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung einer Brennkraftmaschine mit den Merkmalen des Anspruchs 1 vorgeschlagen. Vorteilhafte Weiterbildungen der Hochdruckpumpe werden in den Unteransprüchen angegeben.To solve this problem, a high-pressure pump for a fuel injection device of an internal combustion engine with the features of claim 1 is proposed. Advantageous developments of the high-pressure pump are specified in the subclaims.
Die vorgeschlagene Hochdruckpumpe besitzt wenigstens ein Pumpenelement, das einen Pumpenkolben aufweist, der über einen Nocken oder Exzenter einer Antriebswelle in einer Hubbewegung antreibbar ist, wobei der Pumpenkolben mittelbar über einen Stößel und eine Rolle am Nocken oder Exzenter der Antriebswelle abgestützt ist. Erfindungsgemäß weist die Rolle wenigstens eine zentrale Bohrung auf, die sich entlang der Längsachse A der Rolle erstreckt und zumindest einen kegelförmigen, teilkugelförmigen und/oder teililipsoiden Teilabschnitt zur Ausbildung einer Innenkontur besitzt, die zumindest in einem Teilbereich schräg zur Längsachse A verläuft. Eine derart ausgeführte Rolle zur Abstützung eines Pumpenkolbens an einem Nocken oder Exzenter der Antriebswelle weist den Vorteil auf, dass über die Innenkontur der wenigstens einen zentralen Bohrung die Steifigkeit der Rolle eingestellt werden kann. Denn in den im Wesentlichen hohlzylindrisch ausgebildeten Teilabschnitten weist die Rolle eine geringere Steifigkeit als in den Teilabschnitten auf, die keine zentrale Bohrung besitzen. Die zentrale Bohrung kann sich jedoch auch durch den gesamten Rollenkörper erstrecken, wobei durch Aneinanderreihung kegelförmiger, teilkugelförmiger und/oder teililipsoider Teilabschnitte eine Innenkontur der Bohrung bestimmt werden kann, die zu einer Optimierung der Rollensteifigkeit führt. Zum Einen muss die Rollensteifigkeit hoch genug gewählt werden, um den Pumpenkolben gegenüber dem Nocken bzw. Exzenter zu stützen, zum Anderen sollte sie so gering sein, dass Fehler ohne Ermüdung ausgeglichen werden. Darüber hinaus kann durch eine zentrale Bohrung das Gewicht der Rolle deutlich verringert werden, dies gilt insbesondere, wenn sich die zentrale Bohrung durch den gesamten Rollenkörper erstreckt.The proposed high-pressure pump has at least one pump element which has a pump piston which can be driven in a reciprocating motion via a cam or eccentric of a drive shaft, the pump piston being indirectly supported via a plunger and a roller on the cam or eccentric of the drive shaft. According to the invention, the roller has at least one central bore which extends along the longitudinal axis A of the roller and has at least one conical, partially spherical and / or partially elliptical partial section for forming an inner contour which runs obliquely to the longitudinal axis A at least in a partial region. Such a running roller for supporting a pump piston on a cam or eccentric of the drive shaft has the advantage that over the inner contour of the at least one central bore, the rigidity of the roller can be adjusted. Because in the substantially hollow cylindrical sections formed the roll has a less rigidity than in the sections which do not have a central bore. However, the central bore can also extend through the entire roller body, wherein an inner contour of the bore can be determined by juxtaposing conical, partially spherical and / or partially ellipsoidal sections, which leads to an optimization of the roller stiffness. On the one hand, the roller stiffness must be high enough to support the pump piston against the cam or eccentric, on the other hand, it should be so low that errors are compensated without fatigue. In addition, the weight of the roller can be significantly reduced by a central bore, this is especially true when the central bore extends through the entire roller body.
Ein geringes Gewicht und eine optimierte Rollensteifigkeit führen zu einem verbesserten Andruckverhalten der Rolle am Nocken bzw. Exzenter, so dass die dynamische Belastung im Kontaktbereich der Rolle mit dem Nocken oder dem Exzenter geringer ausfällt. Folglich treten auch weniger Verschleißerscheinungen in diesem Kontaktbereich auf. Die erfindungsgemäße Hochdruckpumpe zeichnet sich daher durch eine lange Lebensdauer aus.A low weight and optimized roller stiffness lead to an improved contact pressure of the roller on the cam or eccentric, so that the dynamic load in the contact area of the roller with the cam or eccentric fails lower. Consequently, less wear occurs in this contact area. The high-pressure pump according to the invention is therefore characterized by a long service life.
Gemäß einem bevorzugten Ausführungsbeispiel ist die wenigstens eine zentrale Bohrung eine Sacklochbohrung, die sich von einer Stirnfläche der Rolle nach innen erstreckt. Vorzugsweise ist - um ein gleichmäßiges Anlaufen der Rolle zu gewährleisten - in beiden Stirnflächen der Rolle eine solche Sacklochbohrung als zentrale Borhung vorgesehen. Dabei sind die beiden Sacklochbohrungen bevorzugt spiegelsymmetrisch in Bezug auf eine Mittelsenkrechte zur Längsachse A ausgebildet, d.h., dass sie sich über einen gleich langen axialen Teilabschnitt a erstrecken und eine Innenkontur besitzen, die gespiegelt ist. Zur Ausbildung der Innenkontur können die beiden Sacklochbohrungen beispielsweise kegelförmig, teilkugelförmig und/oder teilellipsoid ausgebildet sein. Die gespiegelte Ausführung der beiden Sacklochbohrungen trägt ebenfalls zu einem gleichmäßigen Ablaufen der Rolle am Nocken bzw. Exzenter bei und ist daher zu bevorzugen. Das Maß der axialen Erstreckung der beiden Sacklochbohrungen wird den Anforderungen entsprechend gewählt. Die beiden stirnflächenseitig angerodneten Sacklochbohrungen bewirken, dass die Rolle im Bereich ihrer beiden Stirnflächen eine geringere Steifigkeit besitzt, so dass der Anpressdruck der Rolle in diesem Bereich reduziert wird und die Lauffläche am Nocken- bzw. Exzenter aufgrund der geringeren Belastung weniger Laufspuren aufweist. Dies führt weiterhin dazu, dass im Kantenbereich der Rolle Kantendruck verringert wird, so dass auch die Rolle einem geringeren Verschleiß ausgesetzt ist.According to a preferred embodiment, the at least one central bore is a blind hole extending inwardly from an end face of the roller. Preferably - in order to ensure a uniform start of the role - provided in both faces of the role of such a blind hole as a central Borhung. In this case, the two blind holes are preferably formed mirror-symmetrically with respect to a perpendicular bisector to the longitudinal axis A, that is, that they extend over an equally long axial portion a and have an inner contour which is mirrored. To form the inner contour, the two blind holes may be formed, for example, cone-shaped, part-spherical and / or teilellipsoid. The mirrored design of the two blind holes also contributes to a smooth running of the role on the cam or eccentric and is therefore to be preferred. The extent of the axial extent of the two blind holes is selected according to the requirements. The two end face side loosened blind holes cause the role in the region of its two end faces has a lower rigidity, so that the contact pressure of the roller is reduced in this area and the tread on the cam or eccentric due to less load has less tracks. This also leads to the edge area of the roll edge pressure is reduced, so that the role is exposed to less wear.
Vorzugsweise sind die beiden Sacklochbohrungen oder die eine durchgehende zentrale Bohrung derart ausgebildet, dass der Durchmesser von innen nach außen, d.h. zu wenigstens einer Stirnfläche hin, größer wird. Das heißt ferner, dass die Steifigkeit der Rolle zu einer Stirnfläche hin abnimmt. Dies wirkt sich nicht nur günstig auf die Kantenpressung an der Rolle aus, sondern vereinfacht auch die Herstellung einer solchen Rolle. Denn indem der Durchmesser der zentralen Bohrung zu den Stirnflächen hin abnimmt, weist die zentrale Bohrung keine Hinterschneidungen auf. Die zentrale Bohrung kann somit von außen, von einer Stirnfläche aus, gesetzt werden. Alternativ kann die wenigstens eine zentrale Bohrung auch in einem Arbeitsschritt zusammen mit der Rolle hergestellt werden, beispielsweise unter Verwendung einer geschlossenen Form, da das Entformen aufgrund fehlender Hinterschneidungen unproblematisch ist. Darüber hinaus sind aber auch andere Herstellungsverfahren möglich.Preferably, the two blind bores or one central bore are formed such that the diameter from the inside to the outside, i. towards at least one end face, becomes larger. This also means that the rigidity of the roller decreases towards an end face. This not only has a favorable effect on the edge pressure on the roller, but also simplifies the production of such a roller. Because the diameter of the central bore decreases towards the end faces, the central bore has no undercuts. The central bore can thus be set from the outside, from an end face. Alternatively, the at least one central bore can also be produced in one working step together with the roller, for example using a closed mold, since demolding is unproblematic due to the lack of undercuts. In addition, however, other manufacturing methods are possible.
Weiterhin bevorzugt ist die zentrale Bohrung rotationssymmetrisch in Bezug auf die Längsachse A der Rolle ausgebildet. Das heißt, dass die Rolle im Querschnitt im Bereich der zentalen Bohrung umlaufend gleiche Wandungsstärken besitzt. Dadurch ist gewährleistet, dass die Rolle am Nocken bzw. am Exzenter der Antriebswelle gleichmäßig abläuft. Die Formsteifigkeit der Rolle verändert sich demnach lediglich entlang ihrer axialen Erstreckung.Further preferably, the central bore is rotationally symmetrical with respect to the longitudinal axis A of the roller. This means that the roller in the cross section in the area of the central bore has circumferentially equal wall thicknesses. This ensures that the roller runs smoothly on the cam or on the eccentric of the drive shaft. The shape stiffness of the roll thus changes only along its axial extent.
Neben einem kegelförmigen, teilkugelförmigen und/oder teililipsoiden Teilabschnitt a kann die zentrale Bohrung der Rolle auch einen zylinderförmigen Teilabschnitt b besitzen. In diesem Teilabschnitt besitzt die Rolle eine konstante Formsteifigkeit, so dass dieser Teilabschnitt vorzugsweise einen mittleren Teilabschnitt der Rolle bildet. Einen zylinderförmigen Teilabschnitt b kann beispielsweise eine durchgehende zentrale Bohrung aufweisen, die sich von einer Stirnfläche der Rolle zur anderen erstreckt. Der zylinderförmige Teilabschnitt b weist vorzugsweise einen geringeren Durchmesser als ein sich hieran anschließender Teilabschnitt a auf. Auf diese Weise bleibt gewährleistet, dass die Innenkontur keine Hinterschneidungen aufweist. Ein zylindeförmiger Teilabschnitt ist somit besonders einfach herzustellen.In addition to a conical, partially spherical and / or partially ellipsoidal section a, the central bore of the roller can also have a cylindrical section b. In this section, the roller has a constant stiffness, so that this section preferably forms a central portion of the roll. For example, a cylindrical portion b may have a continuous central bore extending from one end face of the roll to the other. The cylindrical section b preferably has a smaller diameter than a subsequent section a. In this way, it is ensured that the inner contour has no undercuts. A cylindric portion is thus particularly easy to manufacture.
Des Weiteren ist bevorzugt vorgesehen, dass die Stirnflächen der Rolle zumindest über einen Teilbereich konvex gewölbt und/oder konisch verlaufend ausgebildet sind. Weist eine Stirnfläche eine zentrale Bohrung auf, besitzt die zumindest teilweise konvex gewölbte und/oder konisch verlaufende Stirnfläche eine zenrale Ausnehmung. Die Stirnfläche kann im Übergang zur zentralen Bohrung gerundet ausgebildet sein. Weist die Rolle an beiden Stirnflächen jeweils eine zentrale Bohrung auf, bilden lediglich die verbleibenden Randbereiche der Stirnflächen, die die jeweilige Bohrung umgeben, Kontaktbereiche zwischen der Rolle und dem Stößel aus.Furthermore, it is preferably provided that the end faces of the roller are convexly curved and / or tapered at least over a partial region. If an end face has a central bore, the at least partially convexly curved and / or conically extending end face has a central recess. The end face may be rounded in the transition to the central bore. If the roller has a central bore on both end faces, only the remaining edge regions of the end faces that surround the respective bore form contact regions between the roller and the tappet.
Gemäß einer bevorzugten Ausführungsform ist die Rolle zumindest teilweise im Stößel aufgenommen, wobei vorzugsweise der Stößel im Bereich der Rollenaufnahme hohlzylindrisch ausgebildet ist, so dass die Stirnflächen der Rolle zumindest teilweise an einer Innenumfangsfläche des Stößels anliegen. Zur weiteren Abstützung kann ferner ein Rollenschuh im Tassenstößel angeordnet sein. Da auch der Rolleschuh im Kontaktbereich mit der Rolle eine dynamische Belastung erfährt, kommen die vorstehend genannten Vorteile auch im Kontaktbereich der Rolle mit dem Rollenschuh zum Tragen.According to a preferred embodiment, the roller is at least partially received in the plunger, wherein preferably the plunger is formed in the region of the roller receiving hollow cylindrical, so that the end faces of the roller at least partially abut an inner peripheral surface of the plunger. For further support, a roller shoe can also be arranged in the tappet. Since the roller shoe also experiences a dynamic load in the area of contact with the roller, the above-mentioned advantages also come into play in the contact area of the roller with the roller shoe.
Die Erfindung wird nachfolgend anhand der beigefügten Zeichnungen näher erläutert. Es zeigen:
- Fig.1
- einen Teillängsschnitt durch ein Pumpenelement einer erfindungsgemäßen Hochdruckpumpe gemäß einer ersten Ausführungsform und
- Fig.2
- einen Längsschnitt durch eine Rolle gemäß einer alternativen Ausführungsform.
- Fig.1
- a partial longitudinal section through a pump element of a high-pressure pump according to the invention according to a first embodiment and
- Fig.2
- a longitudinal section through a roller according to an alternative embodiment.
Das in
Die in
Um ein gleichmäßiges Ablaufen der Rolle 4 auf der Lauffläche 8 des Nockens 2 zu ermöglichen, ist die zentrale Bohrung 5 - unabhängig von der jeweils gewählten Innenkontur - rotationssymmetrisch in Bezug auf die Längsachse A ausgeführt. Das heißt, dass im Querschnitt die Rolle 4 im Bereich der zentralen Bohrung 5 umlaufend die gleiche Wandungsstärke besitzt. Ein gleichmäßiges Ablaufen wird auch dadurch gewährleistet, dass die zentrale Bohrung 5 in Bezug auf eine Mittelachse senkrecht zur Längsachse A spiegelsymmetrisch ausgeführt ist.In order to allow a smooth running of the roller 4 on the
Eine alterantive Ausführungsform der Rolle 4 eines Pumpenelements einer weiteren erfindungsgemäßen Hochdruckpumpe ist in der
Weist die Hochdruckpumpe mehr als ein Pumpenelemenet auf, so besitzt jedes Pumpenelement eine Rolle 4 mit wenigstens einer zentralen Bohrung 5, die eine die Rollensteifigkeit bestimmende Innenkontur besitzt. Bei der Auslegung der Innenkontur findet vorzugsweise auch der Rollenwerkstoff Berücksichtigung.If the high-pressure pump has more than one pump element, each pump element has a roller 4 with at least one
Eine verschleißmindernde Wirkung besitzt die vorgeschlagene Rollenausbildung auch in Bezug auf einen ggf. vorgesehen Rollenschuh 9, an dem die Rolle 4 zusätzlich abgestützt sein kann. Ein Rollenschuh 9 muss jedoch nicht notwendigerweise vorgesehen sein. Die Rolle 4 kann auch über andere Stützelemente zusätzlich am Stößel 3 abgestützt sein.A wear-reducing effect has the proposed role training also in relation to a possibly provided roller shoe 9, on which the roller 4 can be additionally supported. However, a roller shoe 9 need not necessarily be provided. The roller 4 may also be supported via other support elements in addition to the plunger 3.
Claims (7)
- High-pressure pump for a fuel injection device of an internal combustion engine, comprising at least one pump element which has a pump piston (1) which can be driven by a cam (2) or eccentric of a drive shaft in a stroke movement, wherein the pump piston (1) is supported indirectly via a tappet (3) and a roller (4) on the cam (2) or eccentric of the drive shaft, characterized in that the roller (4) has at least one central bore (5) which extends along the longitudinal axis (A) of the roller (4) and has at least one conical, partially conical and/or partially elliptical subportion (a) for forming an inner contour.
- High-pressure pump according to Claim 1, characterized in that the central bore (5) is a blind hole bore which extends inwardly from an end face (6, 6') of the roller (4).
- High-pressure pump according to Claim 1 or 2, characterized in that the diameter of the central bore (5) becomes larger from the inside outwardly, with the result that the stiffness of the roller (4) decreases towards an end face (6, 6').
- High-pressure pump according to one of the preceding claims, characterized in that the central bore (5) is designed in a rotationally symmetrical manner with respect to the longitudinal axis (A) of the roller (4).
- High-pressure pump according to one of the preceding claims, characterized in that the central bore (5) has a cylindrical subportion (b).
- High-pressure pump according to one of the preceding claims, characterized in that the end faces (6, 6') are designed, at least over a subregion, in a convexly curved manner and/or conically extending manner.
- High-pressure pump according to one of the preceding claims, characterized in that the roller (4) is at least partially received in the tappet (3), wherein the tappet (3) is preferably of hollow-cylindrical design in the region of the roller receptacle, with the result that the end faces (6, 6') of the roller (4) bear at least partially against an inner circumferential face (7) of the tappet (3).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009028373A DE102009028373A1 (en) | 2009-08-10 | 2009-08-10 | high pressure pump |
PCT/EP2010/058765 WO2011018260A1 (en) | 2009-08-10 | 2010-06-22 | High-pressure pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2464853A1 EP2464853A1 (en) | 2012-06-20 |
EP2464853B1 true EP2464853B1 (en) | 2014-01-01 |
Family
ID=42710733
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10728173.5A Not-in-force EP2464853B1 (en) | 2009-08-10 | 2010-06-22 | High pressure pump |
Country Status (7)
Country | Link |
---|---|
EP (1) | EP2464853B1 (en) |
JP (1) | JP2013501876A (en) |
KR (1) | KR20120069659A (en) |
CN (1) | CN102472221A (en) |
DE (1) | DE102009028373A1 (en) |
RU (1) | RU2555062C2 (en) |
WO (1) | WO2011018260A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010032056B4 (en) * | 2010-07-23 | 2019-11-28 | Robert Bosch Gmbh | piston unit |
US9835123B2 (en) | 2015-01-13 | 2017-12-05 | Roller Bearing Company Of America, Inc. | Roller for a fuel pump actuator |
KR101730993B1 (en) * | 2016-01-27 | 2017-04-27 | 주식회사 트리보테크 | Plunger pump |
Family Cites Families (15)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CS212800B2 (en) * | 1976-07-15 | 1982-03-26 | Ivan J Cyphelly | Delivery apparatus with hydrostatic torque transfer by cylindrical pistons |
JPS56131021U (en) * | 1980-03-07 | 1981-10-05 | ||
RU2032106C1 (en) * | 1992-01-22 | 1995-03-27 | Рамазан Сабеевич Цаголов | Internal combustion engine with water supply to working fluid |
RU2079695C1 (en) * | 1994-06-22 | 1997-05-20 | Михаил Григорьевич Сандомирский | Fuel pump |
IT1279049B1 (en) * | 1995-10-27 | 1997-12-04 | Eaton Automotive Spa | DIRECT ACTING MECHANICAL PUNTER EQUIPPED WITH A ROLL FOR CONTACT WITH THE CAM OF THE CAMSHAFT OF AN INTERNAL COMBUSTION ENGINE |
CN2560786Y (en) * | 2002-08-10 | 2003-07-16 | 大连铁道学院 | Deep-hole hollow roller bearing |
DE10337847A1 (en) * | 2003-08-18 | 2005-03-17 | Robert Bosch Gmbh | Pump arrangement with a high-pressure pump and a low-pressure pump upstream of this for a fuel injection device of an internal combustion engine |
US7311087B2 (en) * | 2004-11-23 | 2007-12-25 | Cummins Inc. | Fuel pump with a guided tappet assembly and methods for guiding and assembly |
JP2007198518A (en) * | 2006-01-27 | 2007-08-09 | Ntn Corp | Roller and roller bearing |
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 |
DE102006019228A1 (en) * | 2006-04-26 | 2007-10-31 | Schaeffler Kg | Radial rolling bearing, in particular single row ball roller bearing, and method for its assembly |
DE102006045933A1 (en) * | 2006-09-28 | 2008-04-03 | Robert Bosch Gmbh | Plunger assembly for a high pressure pump and high pressure pump with at least one plunger assembly |
JP2008133851A (en) * | 2006-11-27 | 2008-06-12 | Ntn Corp | Roller bearing |
JP2009058033A (en) * | 2007-08-31 | 2009-03-19 | Jtekt Corp | Roller |
CN201103619Y (en) * | 2007-10-22 | 2008-08-20 | 中机洛阳轴承科技有限公司 | Hollow roller for extra-large size bearing |
-
2009
- 2009-08-10 DE DE102009028373A patent/DE102009028373A1/en not_active Withdrawn
-
2010
- 2010-06-22 JP JP2012524165A patent/JP2013501876A/en active Pending
- 2010-06-22 CN CN201080035403XA patent/CN102472221A/en active Pending
- 2010-06-22 EP EP10728173.5A patent/EP2464853B1/en not_active Not-in-force
- 2010-06-22 WO PCT/EP2010/058765 patent/WO2011018260A1/en active Application Filing
- 2010-06-22 RU RU2012108436/06A patent/RU2555062C2/en not_active IP Right Cessation
- 2010-06-22 KR KR1020127003486A patent/KR20120069659A/en not_active Application Discontinuation
Also Published As
Publication number | Publication date |
---|---|
KR20120069659A (en) | 2012-06-28 |
JP2013501876A (en) | 2013-01-17 |
RU2555062C2 (en) | 2015-07-10 |
DE102009028373A1 (en) | 2011-02-17 |
WO2011018260A1 (en) | 2011-02-17 |
RU2012108436A (en) | 2013-10-20 |
EP2464853A1 (en) | 2012-06-20 |
CN102472221A (en) | 2012-05-23 |
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