EP3039281B1 - High-pressure fuel pump or engine valve - Google Patents
High-pressure fuel pump or engine valve Download PDFInfo
- Publication number
- EP3039281B1 EP3039281B1 EP15733402.0A EP15733402A EP3039281B1 EP 3039281 B1 EP3039281 B1 EP 3039281B1 EP 15733402 A EP15733402 A EP 15733402A EP 3039281 B1 EP3039281 B1 EP 3039281B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rod
- axis
- traverse
- pressure
- plunger
- 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.)
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- 239000000446 fuel Substances 0.000 title claims description 19
- 238000004519 manufacturing process Methods 0.000 description 11
- 238000010586 diagram Methods 0.000 description 9
- 238000002485 combustion reaction Methods 0.000 description 8
- 238000007373 indentation Methods 0.000 description 4
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000004049 embossing Methods 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000009931 harmful effect Effects 0.000 description 1
- 239000002655 kraft paper Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000002787 reinforcement Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
- F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0408—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0435—Arrangements for disconnecting the pistons from the actuated cam
-
- 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
- F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
- F04B19/20—Other positive-displacement pumps
- F04B19/22—Other positive-displacement pumps of reciprocating-piston type
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/14—Pistons, piston-rods or piston-rod connections
- F04B53/144—Adaptation of piston-rods
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
-
- 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
-
- 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
- F02M2200/03—Fuel-injection apparatus having means for reducing or avoiding stress, e.g. the stress caused by mechanical force, by fluid pressure or by temperature variations
Definitions
- the invention relates to a pressure influencing device for influencing a pressure in a medium, such as an engine valve or a high-pressure fuel pump.
- a rod is often present, which is driven by a plunger.
- the plunger in turn is driven, for example, in the case of a piston pump as a high-pressure fuel pump by a camshaft of an internal combustion engine.
- Fig. 12 shows a schematic representation of a driven by a plunger 10 rod 12.
- the in Fig. 12 The arrangement shown can be used both in, for example, a piston pump 14 as a high-pressure fuel pump 16 and in engine valves 18. In both cases - high-pressure fuel pump 16 and engine valve 18 - is by a movement of the rod 12 - which in the case of the piston pump 14 is a piston 20 - a pressure in an in Fig. 12 arranged above the piston 20, not shown space at a first end portion 22 of the rod 12 influenced.
- the motor valve 18 is opened and closed by the movement of the rod 12 along a rod axis 26 and thus released when opening a pressure or built 18 upon pressure when closing the engine valve.
- Fig. 12 shown arrangement both when used in a piston pump 14 as well as when used in an engine valve 18 is a pressure influencing device 28.
- the pressure influencing device 28 in FIG Fig. 12 has a rod guide 30 for guiding the rod 12 and a tappet guide 32 for guiding the plunger 10.
- the plunger 10 is constructed from a plunger shirt 34 and a cross member 36 and the cross member 36 is connected via the plunger shirt 34 with a roller 38 in contact.
- a camshaft moves the roller 38 along a ram guide axis 50, which in Fig. 12 coincides with the rod guide axis 52, up and down, the roller 38 transmits this upward and downward movement on the crossbar 36.
- Traverse 36 is in contact with rod 12 at a second end portion 42 of rod 12 and further transmits the upward and downward movement to rod 12 so that it has a first end portion 22 pressure in one above first end portion 22 of FIG Rod 12 arranged can influence, not shown space.
- a flange 44 is shown schematically with which the pressure-influencing device 28 can be attached, for example, to a motor housing.
- WO 2008/068116 A1 JP 2000 179 308 A1 .
- DE 10 2007 022 220 A1 and DE 10 2007 057 911 A1 each describe a piston which rests on a cross member in a plunger and is driven by the plunger in a translatory movement.
- the piston has a dome-shaped end region in the contact region in which it is in contact with the crossbeam, while the crossbeam has a dome-shaped bulge in this contact region.
- the object of the invention is therefore to provide an improved in this respect pressure influencing device.
- a pressure-influencing device for influencing a pressure in a medium has a rod with a first end region for defining a space having the medium, wherein the rod is movably arranged along a rod axis between a first top dead center and a second bottom dead center. Further, a plunger is provided with a cross member disposed substantially perpendicular to a plunger axis for transmitting kinetic energy from a plunger drive to the rod in a contact area of a truss surface and a second end portion of the rod opposite to the first end portion. In the contact region, the rod has a dome-shaped end region and the traverse also has a dome-shaped bulge.
- the second end portion of the rod is formed by the dome-shaped end portion.
- top dead center is meant a position of the rod in which the rod is urged by a drive, such as a camshaft, to its highest deflection point along the rod axis relative to an axis of, for example, the camshaft.
- a drive such as a camshaft
- bottom dead center is to be understood as the point at which the rod is closest to the axis of, for example, the camshaft.
- the pressure-influencing device can be a high-pressure fuel pump or an engine valve. In the case of the high-pressure fuel pump, the rod is then formed by the piston.
- a high pressure fuel pump for pressurizing a fuel therefore has a piston movably disposed between a first top dead center and a second bottom dead center along a piston axis, and a ram having a substantially perpendicular to one Plunger axis arranged traverse for transmitting kinetic energy from a plunger drive on the piston in a contact region of a truss surface and an end portion of the piston.
- the piston In the contact region, the piston has a dome-shaped end region and the traverse also has a dome-shaped bulge.
- the rod with its dome-shaped rod end no longer moves on a flat traverse, but in a dome-shaped trench, ie the previous "dome-surface contact" is replaced by a "dome-dome contact".
- a dome namely a spherical cap
- a smaller radius can be selected at the dome-shaped end region of the rod.
- the angular error ⁇ is thereby completely eliminated. Only a slight coaxial error between a rod axis and a center of the dome shape remains. This has a positive effect on the transverse forces and the resulting moments, since the contact angle ⁇ 1 or ⁇ 2 and the lever arms a 1 and a 2 are reduced.
- a contact point K between the cross member and the rod shifts from an outer edge region of the dome-shaped end portion of the rod to the rod axis.
- the described lever arms a 1 and a 2 define the distances between the contact point K and a tappet guide axis or a rod guide axis, and the contact angles ⁇ 1 , ⁇ 2 , the angles of a normal to the crossbar at the contact point K to a rod axis or Define a ram axis, significantly reduced.
- the traverse in adjacent to the dome-shaped bulge areas on a substantially perpendicular to the plunger axis flat trained truss surface.
- the region of the truss surface which comes into contact with the dome-shaped end region of the rod is preferably not completely dome-shaped, but additionally has even partial regions. This contributes advantageously to the reinforcement of the traverse as a whole.
- the dome-shaped bulge can be generated in the truss surface by being introduced by embossing in a flat truss surface.
- an advantageously cost-effective realization of the truss surface geometry can be achieved.
- the dome-shaped indentation is arranged symmetrically about an axis which halves the cross-piece perpendicular to its longitudinal axis.
- the dome-shaped bulge is advantageously arranged symmetrically overall on the side of the traverse, which comes into contact with the dome-shaped end region of the rod.
- a defined position of a center point of the dome-shaped bulge can advantageously be generated on the traverse, which in turn leads to an advantageously defined guidance of the rod by the traverse.
- the Traverse is arranged to be movable radially to the plunger axis, wherein the traverse is inserted in particular without radial attachment in the plunger.
- the coaxial errors can advantageously be compensated via the radially movable traverse. Because the coaxial errors are advantageous only a very small proportion of the lever arms a 1 and a 2 , it is preferably a static position error of the dome shape.
- the coaxial errors are advantageous only a very small proportion of the lever arms a 1 and a 2 , it is preferably a static position error of the dome shape.
- movable radially to the ram traverse cross member therefore preferably finds the traverse within the first strokes of the rod their position and thus can preferably compensate for the static position error.
- a bulge radius of the dome-shaped bulge of the traverse is greater than a rod radius of the dome-shaped end region of the rod.
- a rod guide having a rod guide axis, wherein a rod end radius of the dome-shaped end portion of the rod is less than or equal to a distance at the top dead center of the rod from a tangent to a rod dome surface on the rod axis to an intersection of the ram axis and the rod guide axis ,
- the distance between the tangent to the dome-shaped end portion of the rod in the point where the rod axis intersects an outer surface of the rod and an intersection of the ram axis with the rod guide axis varies during operation of the rod.
- the distance is smaller at top dead center of the rod than at bottom dead center and all operating states in between. That is, the radius of the dome-shaped end portion of the rod is preferably less than or equal to the smallest distance between the intersection of the guide axes and a smallest protrusion of the rod end - in the position at top dead center - selected.
- the pressure-influencing device may advantageously be a high-pressure fuel pump, but it may alternatively also be an engine valve.
- Fig. 1 shows an internal combustion engine 56, to which via a flange 44, a pressure-influencing device 28 is attached in the form of a high-pressure fuel pump 16.
- the pressure-influencing device 28 has a tappet 10 with a tappet guide 32, a tappet shirt 34 and a cross-member 36. Furthermore, the pressure-influencing device 28 has a rod 12 in the form of a piston 20 and a rod guide 30.
- Fig. 2 shows a pressure influencing device 28 with plunger 10 and plunger guide 32 and plunger shirt 34 and with rod guide 30 and rod 12.
- internal combustion engine 56 no flange 44 is provided.
- Fig. 3 is the pressure-influencing device off Fig. 1 with flange 44, which forms a flange 58, shown schematically.
- the pressure-influencing device 28 in the form of the high-pressure fuel pump 16 has the plunger 10 with plunger guide 30, plunger shirt 34 and cross member 36 and the rod 12 with rod guide 30.
- the rod 12 of the traverse 36 is between a first top dead center 60 and a second bottom dead center 62 along a rod axis 26 driven, that is, moved up and down.
- the traverse 36 in turn is driven by a arranged below the cross member 36 roller 38 along a ram axis 40, which in the in Fig. 3 shown idealized representation of the pressure influencing device 28 coincides with the rod axis 26.
- the roller 38 is driven via a camshaft 65 of the internal combustion engine 56.
- roller 38 and the camshaft 65 thus together form a plunger drive 66th
- ram axis 40 and the rod axis 26 coincide, but also a ram guide axis 50, ie the axis of the ram guide 32, and a rod guide axis 52, ie the axis of the rod guide 30.
- the rod 12, and the piston 20 has a game in the rod guide 30, as well as the plunger 10 has a game in the ram guide 32.
- the cross member 36 is movably supported in the plunger shirt 34, which is indicated by the arrows P, and is movable radially to the plunger shaft 40 in all directions.
- the crossbar 36 and the rod 12 contact punctiform in a contact region 68 of a truss surface 70 and a second end portion 42 of the rod 12, which is opposite to a first end portion 22.
- the traverse has a dome-shaped bulge 72 and the rod 12 has a dome-shaped end region 74.
- the dome-shaped bulge 72 does not span the entire truss surface 70, but the traverse 36 has adjacent to the dome-shaped bulge 72 a perpendicular to the ram axis 40 flat trained truss surface.
- the dome-shaped bulge 72 can be introduced into the truss surface 70 by embossing, for example.
- the dome-shaped indentation 72 is arranged symmetrically on the truss surface 70, so that the lowest point of the dome-shaped indentation 72 is cut by the ram axis 40, which runs perpendicular to a longitudinal axis 76 of the traverse 36.
- Fig. 3 shows only an idealized representation of the pressure influencing device 28, while in Fig. 4 the actual prevailing conditions are shown oversubscribed.
- the plunger guide axis 50 and the rod guide axis 52 or the plunger axis 40 and the rod axis 26 do not coincide, so that in addition to a force acting perpendicular to the rod 12 axial force F a transverse forces act.
- a transverse forces act.
- Fig. 7 Turns off the situation of the Druckbeinlungs liked 28 Fig. 5 schematically in a geometric arrangement.
- the play was not shown in the guides 30, 32 and the coaxial error in an intersection S between the rod axis 26 and ram axis 40, because these errors are usually very small in relation to the errors shown.
- the traverse 36 can have an angular error ⁇ both in the positive and in the negative direction.
- Fig. 8 adjusts the situation of pressure control 28 according to Fig. 6 geometrically
- Hertzian pressures are kept constant without limiting the manufacturing tolerances. This can be done by advantageous choice of the radii of dome-shaped bulge 72 and dome-shaped end portion 74.
- Distinguishing criterion is the condition that the Hertzian pressure compared to an arrangement of the pressure influencing device 28, as shown in Fig. 5 shown should not be enlarged. From this, it is determined whether a rod end radius 84 of the dome-shaped end portion 74 of the rod 12 can be made smaller than or equal to a minimum distance a min at the top dead center 60 of the rod 12 between a tangent T on a rod dome surface 86 at the point of the rod axis 26 Intersection point S of the ram axis 40 and the rod guide axis 52nd
- a bulge radius 88 of the dome-shaped bulge 72 of the traverse 36 is greater than the rod end radius 84.
- the traverse 36 is provided with sufficient rigidity. It can thereby be achieved that the contact point K is always between the axes 50, 52 and a very small spread between "worst case” and “best case” tolerances can be realized.
- Fig. 9 illustrates various situations of the rod end radius 84 for the first case.
- Rod ends 48 are shown with three different rod end radii 84.
- a stroke 90 of the rods 12 is indicated.
- the contact point 82 of the rod 12 with the largest rod end radius 84 is clearly spaced from the rod axis 26. The smaller the rod end radius becomes, the smaller is this distance a 2 .
- the contact angle ⁇ and thus the lateral forces acting on the pressure-influencing devices 28 are also reduced.
- the rod end radius 84 is chosen to be greater than a min . Also this constellation represents a clear improvement to the situation in Fig. 5 as long as the bulge radius 88 has a minimum radius that is significantly greater than the rod end radius 84.
- Fig. 11 shows a diagram illustrating the lateral force acting on the pressure influencing device 28, depending on the axial load F a .
- Diagram A shows the force relationships for a pressure-influencing device 28 without a dome-shaped bulge 72 in the crossbeam 36 for the "best case" situation, which is shown in FIG Fig. 7 with the riot 82 is shown.
- the diagram C sets the situation for a pressure-influencing device 28 without a dome-shaped bulge 72 for the "worst case” scenario contact point 78 in FIG Fig. 7 - dar.
- Diagram B shows the force relationships for a pressure-influencing device 28, which has a dome-shaped bulge 72 in the crossmember 36.
- the traverse 36 in the diagram B has a radial mobility to the ram axis 40.
- Diagram D shows the situation of a pressure-influencing device 28 with the dome-shaped bulge 72, when the traverse 36 is fixed and is not movable radially to the ram axis 40.
- dome-shaped bulge 72 and movable cross-member 36 provides significantly better balance of power than the "worst case” scenario of the pressure influencing device 28 without dome-shaped bulge 72. Since the achievement of "worst case” and “best case “is not controllable and the flow of forces in the diagram B comes close to the 'best case' case, results in a more controllable balance of power in a pressure influencing device 28 with dome-shaped bulge 72. At the same time, however, the differences between the diagrams B and D show that a radially movable 36 is clearly favored.
- the dome-shaped bulge 72 generates direction-independent transverse forces, which are at a low level between the "best case” and “worst case” of the pressure-influencing device 28 according to the prior art. This corresponds to a general reduction of the prevailing lateral forces.
- the transverse forces resulting from the axial forces F a due to geometric discontinuities of the components can be reduced by up to 40% in comparison to the "worst case" constellation of the prior art.
- the harmful effects of the lateral forces by the contact angle ⁇ 1 , ⁇ 2 can be largely eliminated, resulting in a reduction of the lateral forces.
- the perpendicularity of the traverse 36 to the ram axis 40 is almost irrelevant, which leads to a reduction in manufacturing costs.
- the dome-shaped bulge 72 of the traverse 36 can be produced by simple stamping, which is particularly cost-effective.
- the angle error ⁇ is completely eliminated and the scattering and magnitude of the total angle error ⁇ 1 or ⁇ 2 is considerably reduced, so that the design can be expected to have almost constant loads and "best case” or “worst case” advantageous close together lie.
- the rod radius 84 and the bulge radius 88, ⁇ 1 and ⁇ 2, respectively may be kept even smaller than the unavoidable angular error ⁇ between the axes 50, 52 of the guides.
- the dome-shaped bulge 72 can of course also be provided in a separate sliding shoe which is arranged in the tappet 10.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Geometry (AREA)
- Fuel-Injection Apparatus (AREA)
- Reciprocating Pumps (AREA)
Description
Die Erfindung betrifft eine Druckbeeinflussungseinrichtung zum Beeinflussen eines Druckes in einem Medium, wie beispielsweise ein Motorventil bzw. eine Kraftstoffhochdruckpumpe.The invention relates to a pressure influencing device for influencing a pressure in a medium, such as an engine valve or a high-pressure fuel pump.
Sowohl bei Motorventilen als auch bei beispielsweise Kolbenpumpen, die als Kraftstoffhochdruckpumpen zum Pumpen von Kraftstoff verwendet werden, ist häufig eine Stange vorhanden, die durch einen Stößel angetrieben wird. Der Stößel seinerseits wird beispielsweise im Falle einer Kolbenpumpe als Kraftstoffhochdruckpumpe von einer Nockenwelle einer Brennkraftmaschine angetrieben.Both engine valves and, for example, piston pumps which are used as high-pressure fuel pumps for pumping fuel, a rod is often present, which is driven by a plunger. The plunger in turn is driven, for example, in the case of a piston pump as a high-pressure fuel pump by a camshaft of an internal combustion engine.
Im Falle der Kolbenpumpe 14 wird Kraftstoff durch die Bewegung des Kolbens 20 entlang einer Kolbenachse 24 mit Druck beaufschlagt.In the case of the
Im Falle eines Motorventils 18 wird durch die Bewegung der Stange 12 entlang einer Stangenachse 26 das Motorventil 18 geöffnet und geschlossen und somit beim Öffnen ein Druck abgelassen bzw. beim Schließen des Motorventils 18 Druck aufgebaut.In the case of an
Insgesamt stellt daher die in
Die Druckbeeinflussungseinrichtung 28 in
In
Allgemein entstehen bei einer durch den Stößel 10 angetriebenen Stange 12 - beispielsweise in Motorventilen 18 oder auch bei Kolbenpumpen 14 - in einem Kontaktpunkt 46 zwischen einem Stangenende 48 im zweiten Endbereich 42 der Stange 12 und der Traverse 36 des Stößels 10 erhebliche Kontaktkräfte. Dies wird einerseits verursacht durch die Axiallast Fa, andererseits jedoch auch über geometrische Toleranzen der einzelnen Bauteile der Druckbeeinflussungseinrichtung 28 und dem jeweiligen Spiel der einzelnen Elemente in der Druckbeeinflussungseinrichtung 28.Generally arise in a driven by the
Im Einzelnen wirken die folgenden Kräfte:
- Die Hertz'sche Pressung bzw. der Hertz'sche Kontakt (Fa, siehe
Fig. 12 ) durch die Axialkraft Fa, die eine Abplattung der miteinander in Kontakt stehenden Flächen bewirkt und, sodass statt eines idealen punktförmigen Kontaktes eine Kontaktfläche mit vergrößerter Kontaktfläche vorherrscht; - Querkräfte (siehe in
Fig. 13 ), die aus einem Winkelfehler α zwischen einerStößelführungsachse 50 und derStangenachse 26 resultieren; - Querkräfte durch den Aufstandswinkel β1 zwischen der
Stangenachse 26 und der Normalen im Aufstandspunkt der Traverse 36 auf die Stange 12 (sieheFig. 13 ); - Querkräfte durch den Aufstandswinkel β2 zwischen der Stößelachse 40 und der Normalen im Aufstandspunkt der Traverse 36 auf den Stößel 10 (siehe
Fig. 13 ); - Aufstandsmomente als Produkt aus der Axiallast Fa und den Abständen a1 bzw. a2 eines Kontaktpunktes K von Traverse 36 zu Stange 12 zu der
Stößelführungsachse 50 bzw. einer Stangenführungsachse 52 (vgl.Fig. 13 ). Die Aufstandsmomente werden hervorgerufen durch die Aufstandswinkel β1 und β2, den Koaxialfehler der beiden 50, 52, d. h. dem Winkelfehler α, und den Abstand zwischen derFührungsachsen Stößelführungsachse 50 und einem Schnittpunkt S einerFlanschfläche 54 desFlansches 44 mit derStangenführungsachse 52.
- The Hertzian pressure or the Hertzian contact (F a , see
Fig. 12 ) by the axial force F a , which causes a flattening of the surfaces in contact with each other, and so that instead of an ideal point-like contact, a contact surface with an enlarged contact surface prevails; - Transverse forces (see in
Fig. 13 ) resulting from an angular error α between atappet guide axis 50 and therod axis 26; - Transverse forces due to the contact angle β 1 between the
rod axis 26 and the normal in the contact point of thecross member 36 on the rod 12 (seeFig. 13 ); - Transverse forces by the contact angle β 2 between the
plunger axis 40 and the normal in the contact point of thecrossbar 36 on the plunger 10 (seeFig. 13 ); - Upright torques as a product of the axial load F a and the distances a 1 and a 2 of a contact point K of
traverse 36 torod 12 to theplunger guide shaft 50 and a rod guide axis 52 (see.Fig. 13 ). The contact torque is caused by the contact angle β 1 and β 2 , the coaxial error of the two 50, 52, ie the angular error α, and the distance between theguide axes ram guide axis 50 and an intersection S of aflange 54 of theflange 44 with the rod guide axis 52nd
All diese Kräfte führen sowohl in der Stößelführung 32 als auch in der Stangenführung 30 zu erheblichen Lagerreaktionskräften, welche zu Verschleiß und schließlich zum Fressen der Linear- bzw. Gleitführungen führen können. Die maximal zulässigen Lagerreaktionskräfte in den Führungen 50, 52 bestimmen die maximal zulässigen Fehler des Gesamtsystems.All these forces lead both in the
Bisher wurde zur Verbesserung des Systems mit engen Toleranzen mit hohen Herstellungskosten bzw. mit einer Erhöhung der Führungslängen gearbeitet. Die einzelnen Kräfte werden dabei folgendermaßen beeinflusst:
- Um die Hertz'sche Pressung und den Winkelfehler α zwischen den
50, 52 kompensieren zu können, wird einFührungsachsen balliges Stangenende 48 in Kalottenform verwendet. Daskalottenförmige Stangenende 48 wird, wie inFig. 13 gezeigt, auf eineebene Traverse 36 gestellt. Die Ebenheit der Traverse 36 lässt sowohl eine konvexe als auch konkave Fläche zu, was zu einer erheblichen Streuung der Hertz'schen Pressung führt. Zur Erzielung von zulässigen Hertz'schen Pressungen müssen daher entweder die Toleranzen für die Ebenheit und/oder die Toleranzen für die Form deskalottenförmigen Stangenendes 48 reduziert werden, was mit einer Erhöhung der Herstellungskosten einhergeht. Weiter ist es auch möglich, den Radius deskalottenförmigen Stangenendes 48 zu vergrößern, wodurch jedoch das Aufstandsmoment steigt. Zur Kompensation müssen daher wiederum die Toleranzen eingeschränkt werden, was ebenfalls zur Erhöhung der Herstellungskosten führt. - Querkräfte aus dem Winkelfehler α können nur durch Einschränkung der Toleranzen reduziert werden, was mit höheren Fertigungskosten einhergeht. Die daraus resultierenden Querkräfte können auch durch eine geringere Steifigkeit bzw. Querfederrate der
Stange 12 reduziert werden, was aufgrund der Axiallast Fa und der erforderlichen Bauteilfestigkeit zumeist nur schwer erreichbar ist. - Der Winkelfehler insgesamt ist die Summe aus dem Winkelfehler α zwischen den
50, 52, den Führungspielen (d. h. Verkippen desFührungsachsen Stößels 10 in derStößelführung 32 bzw. derStange 12 in der Stangenführung 30), und der Rechtwinkligkeit γ der Traverse 36, d. h. dem Winkelfehler der Traverse 36 zum Führungsdurchmesser desStößels 10, d. h. des Stößelhemdes 34. Die Summe dieser Winkelfehler sind die Aufstandswinkel β1 und β2. Die resultierende Querkraft auf dieStange 12 berechnet sich über den Term sin β1 x Fa. Die resultierende Querkraft auf denStößel 10 berechnet sich über den Term sin β2 x (Fa x 1/cosα). Diese Querkräfte können nur durch Reduzierung der Toleranzen und/oder in bedingtem Maße durch Erhöhung der Führungslängen reduziert werden. Beides führt jedoch zur Erhöhung der Herstellungskosten. - Die Hebelarme a1 und a2 zu den
50, 52 resultieren aus den Koaxialfehlern derFührungsachsen 50, 52 zueinander und den Aufstandswinkeln β1 bzw. β2, welche aus den Winkelfehlern α, γ und dem Radius desFührungen kalottenförmigen Stangenendes 48 resultieren. Dies führt zum radialen Auswandern des Kontaktpunktes K und erzeugt die Hebelarme a1 und a2. Zur Reduzierung der Hebelarme a1 und a2 können entweder die Toleranzen der Koaxialfehler oder des Radius deskalottenförmigen Stangenendes 48 eingeschränkt werden. Dies führt jedoch zu keiner großen Verbesserung und dennoch steigenden Herstellungskosten. Alternativ kann auch der Nennwert des Radius deskalottenförmigen Stangenendes 48 verkleinert werden, was jedoch meist aufgrund der Hertz'schen Pressungen nur schwer möglich ist.
- In order to be able to compensate for the Hertzian pressure and the angular error α between the
50, 52, a crownedguide shafts rod end 48 in a spherical shape is used. The dome-shaped rod end 48 becomes, as inFig. 13 shown, placed on a flat Traverse 36. The flatness of thetraverse 36 allows both a convex and a concave surface, resulting in a significant dispersion of the Hertzian pressure. Therefore, in order to obtain allowable Hertzian stresses, either the tolerances for the flatness and / or the tolerances for the shape of the dome-shapedrod end 48 must be reduced, which leads to an increase in the production costs. Further, it is also possible to increase the radius of the dome-shapedrod end 48, whereby, however, the contact torque increases. For compensation, therefore, in turn, the tolerances must be limited, which also leads to an increase in manufacturing costs. - Transverse forces from the angle error α can only be reduced by limiting the tolerances, which is associated with higher production costs. The resulting transverse forces can also be reduced by a lower stiffness or transverse spring rate of the
rod 12, which is usually difficult to achieve due to the axial load F a and the required component strength. - The angular error total is the sum of the angular error α between the
50, 52, the guide plays (ie tilting of theguide shafts plunger 10 in theplunger guide 32 and therod 12 in the rod guide 30), and the squareness γ of thecrossbar 36, ie the Angular error of thecross member 36 to the guide diameter of theplunger 10, ie theplunger shirt 34. The sum of these angle errors are the contact angle β 1 and β. 2 The resulting lateral force onrod 12 is calculated by the term sin β 1 x F a . The resulting lateral force on theplunger 10 is calculated by the term sin β 2 x (F a x 1 / cos α). These lateral forces can only be reduced by reducing the tolerances and / or to a limited extent by increasing the guide lengths. However, both leads to an increase in production costs. - The lever arms a 1 and a 2 to the guide axes 50, 52 resulting from the coaxial errors of the
50, 52 to each other and the Aufstandsswinkeln β 1 and β 2 , which result from the angular errors α, γ and the radius of the dome-shapedguides rod end 48. This leads to the radial emigration of the contact point K and generates the lever arms a 1 and a 2 . To reduce the lever arms a 1 and a 2 , either the tolerances of the coaxial errors or the radius of the dome-shapedrod end 48 can be restricted. However, this leads to no great improvement and yet increasing production costs. Alternatively, the nominal value of the radius of the dome-shapedrod end 48 can be reduced, which, however, is only possible with difficulty due to the Hertzian pressure.
Insgesamt können daher die erheblichen Kontaktkräfte, die in einem Aufbau nach dem Stand der Technik gemäß
Aufgabe der Erfindung ist es daher, eine in dieser Hinsicht verbesserte Druckbeeinflussungseinrichtung bereitzustellen.The object of the invention is therefore to provide an improved in this respect pressure influencing device.
Diese Aufgabe wird durch eine Druckbeeinflussungseinrichtung mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a pressure-influencing device having the features of claim 1.
Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der abhängigen Ansprüche.Advantageous embodiments of the invention are the subject of the dependent claims.
Eine Druckbeeinflussungseinrichtung zum Beeinflussen eines Druckes in einem Medium weist eine Stange mit einem ersten Endbereich zum Begrenzen eines das Medium aufweisenden Raumes auf, wobei die Stange entlang einer Stangenachse zwischen einem ersten, oberen Totpunkt und einem zweiten, unteren Totpunkt beweglich angeordnet ist. Weiter ist ein Stößel mit einer im Wesentlichen senkrecht zu einer Stößelachse angeordneten Traverse zum Übertragen von kinetischer Energie von einem Stößelantrieb auf die Stange in einem Kontaktbereich von einer Traversenoberfläche und einem zweiten Endbereich der Stange, der gegenüberliegend zu dem ersten Endbereich angeordnet ist, vorgesehen. In dem Kontaktbereich weist die Stange einen kalottenförmigen Endbereich und die Traverse eine ebenfalls kalottenförmige Ausbuchtung auf.A pressure-influencing device for influencing a pressure in a medium has a rod with a first end region for defining a space having the medium, wherein the rod is movably arranged along a rod axis between a first top dead center and a second bottom dead center. Further, a plunger is provided with a cross member disposed substantially perpendicular to a plunger axis for transmitting kinetic energy from a plunger drive to the rod in a contact area of a truss surface and a second end portion of the rod opposite to the first end portion. In the contact region, the rod has a dome-shaped end region and the traverse also has a dome-shaped bulge.
Somit ist der zweite Endbereich der Stange durch den kalottenförmigen Endbereich gebildet.Thus, the second end portion of the rod is formed by the dome-shaped end portion.
Unter dem "oberen Totpunkt" soll eine Position der Stange verstanden werden, in der die Stange von einem Antrieb, beispielsweise einer Nockenwelle, an ihren höchsten Auslenkungspunkt entlang der Stangenachse relativ zu einer Achse von beispielsweise der Nockenwelle gedrückt ist. Analog ist unter dem Begriff "unterer Totpunkt" der Punkt zu verstehen, an dem sich die Stange am dichtesten an der Achse von beispielsweise der Nockenwelle befindet.By "top dead center" is meant a position of the rod in which the rod is urged by a drive, such as a camshaft, to its highest deflection point along the rod axis relative to an axis of, for example, the camshaft. Analogously, the term "bottom dead center" is to be understood as the point at which the rod is closest to the axis of, for example, the camshaft.
Die Druckbeeinflussungseinrichtung kann dabei eine Kraftstoffhochdruckpumpe oder ein Motorventil sein. Im Falle der Kraftstoffhochdruckpumpe ist dann die Stange durch den Kolben gebildet.The pressure-influencing device can be a high-pressure fuel pump or an engine valve. In the case of the high-pressure fuel pump, the rod is then formed by the piston.
Eine Kraftstoffhochdruckpumpe zum Beaufschlagen eines Kraftstoffes mit Druck weist daher einen zwischen einem ersten, oberen Totpunkt und einem zweiten, unteren Totpunkt entlang einer Kolbenachse beweglich angeordneten Kolben, sowie einen Stößel mit einer im Wesentlichen senkrecht zu einer Stößelachse angeordneten Traverse zum Übertragen von kinetischer Energie von einem Stößelantrieb auf den Kolben in einen Kontaktbereich von einer Traversenoberfläche und einem Endbereich des Kolbens auf. In dem Kontaktbereich weist der Kolben einen kalottenförmigen Endbereich und die Traverse eine ebenfalls kalottenförmige Ausbuchtung auf.A high pressure fuel pump for pressurizing a fuel therefore has a piston movably disposed between a first top dead center and a second bottom dead center along a piston axis, and a ram having a substantially perpendicular to one Plunger axis arranged traverse for transmitting kinetic energy from a plunger drive on the piston in a contact region of a truss surface and an end portion of the piston. In the contact region, the piston has a dome-shaped end region and the traverse also has a dome-shaped bulge.
Durch die beschriebene Anordnung bewegt sich nun die Stange mit ihrem kalottenförmigen Stangenende nicht mehr auf einer ebenen Traverse, sondern in einem kalottenförmigen Graben, d. h. der bisherige "Kalotten-Flächen-Kontakt" wird durch einen "Kalotten-Kalotten-Kontakt" ersetzt. Dabei wird in die bisher ebene Fläche der Traverse eine Kalotte, nämlich eine Kugelkalotte, eingebracht. Dadurch kann bei gleicher Hertz'scher Pressung ein kleinerer Radius am kalottenförmigen Endbereich der Stange gewählt werden. Der Winkelfehler γ wird dadurch vollständig eliminiert. Lediglich ein geringfügiger Koaxialfehler zwischen einer Stangenachse und einem Mittelpunkt der Kalottenform bleibt zurück. Dies wirkt sich positiv auf die Querkräfte und die resultierenden Momente aus, da die Aufstandswinkel β1 bzw. β2 und die Hebelarme a1 und a2 reduziert werden.As a result of the described arrangement, the rod with its dome-shaped rod end no longer moves on a flat traverse, but in a dome-shaped trench, ie the previous "dome-surface contact" is replaced by a "dome-dome contact". In this case, a dome, namely a spherical cap, is introduced into the hitherto flat surface of the traverse. As a result, with the same Hertzian pressure, a smaller radius can be selected at the dome-shaped end region of the rod. The angular error γ is thereby completely eliminated. Only a slight coaxial error between a rod axis and a center of the dome shape remains. This has a positive effect on the transverse forces and the resulting moments, since the contact angle β 1 or β 2 and the lever arms a 1 and a 2 are reduced.
Denn durch die kalottenförmige Ausbuchtung in der Traverse verschiebt sich ein Kontaktpunkt K zwischen der Traverse und der Stange von einem äußeren Randbereich des kalottenförmigen Endbereiches der Stange zur Stangenachse hin. Dadurch werden die beschriebenen Hebelarme a1 und a2, die Abstände zwischen dem Kontaktpunkt K und einer Stößelführungsachse bzw. einer Stangenführungsachse definieren, sowie die Aufstandswinkel β1, β2, die Winkel jeweils einer Normalen auf die Traverse im Kontaktpunkt K zu einer Stangenachse bzw. einer Stößelachse definieren, deutlich verkleinert.For through the dome-shaped bulge in the cross member, a contact point K between the cross member and the rod shifts from an outer edge region of the dome-shaped end portion of the rod to the rod axis. As a result, the described lever arms a 1 and a 2 define the distances between the contact point K and a tappet guide axis or a rod guide axis, and the contact angles β 1 , β 2 , the angles of a normal to the crossbar at the contact point K to a rod axis or Define a ram axis, significantly reduced.
Dadurch können die zwischen den Elementen wirkenden Kontaktkräfte deutlich reduziert werden, ohne jedoch Toleranzen und Führungslängen zu stark zu verändern, so dass insgesamt eine verbesserte Übertragung einer kinetischen Energie von dem Stößel auf die Stange erreicht werden kann, ohne dabei die Herstellungskosten zu stark zu erhöhen.As a result, the contact forces acting between the elements can be significantly reduced, but without changing tolerances and guide lengths too much, so that overall an improved transmission of kinetic energy from the plunger to the rod can be achieved without increasing the manufacturing cost too much.
Vorzugsweise weist die Traverse in an die kalottenförmige Ausbuchtung angrenzenden Bereichen eine im Wesentlichen senkrecht zur Stößelachse eben ausgebildete Traversenoberfläche auf. Somit ist der Bereich der Traversenoberfläche, der in Kontakt kommt mit dem kalottenförmigen Endbereich der Stange, vorzugsweise nicht vollständig kalottenförmig ausgebildet, sondern weist zusätzlich noch ebene Teilbereiche auf. Dies trägt vorteilhaft zur Verstärkung der Traverse insgesamt bei. Zusätzlich kann es jedoch noch vorteilhaft sein, wenn weitere Maßnahmen zur Versteifung der Traverse ergriffen werden, beispielsweise wenn die Traverse im Vergleich zu einer Traverse aus dem Stand der Technik parallel zur Stößelachse dicker ausgebildet oder aus einem steiferen Material gebildet wird.Preferably, the traverse in adjacent to the dome-shaped bulge areas on a substantially perpendicular to the plunger axis flat trained truss surface. Thus, the region of the truss surface which comes into contact with the dome-shaped end region of the rod is preferably not completely dome-shaped, but additionally has even partial regions. This contributes advantageously to the reinforcement of the traverse as a whole. In addition, however, it may still be advantageous if further measures are taken to stiffen the traverse, for example, when the traverse formed thicker in comparison to a traverse of the prior art parallel to the ram axis or formed of a stiffer material.
Besonders vorteilhaft kann die kalottenförmige Ausbuchtung in der Traversenoberfläche erzeugt werden, indem sie durch Prägen in eine ebene Traversenoberfläche eingebracht wird. Dadurch kann eine vorteilhaft kostengünstige Realisierung der Traversenoberflächengeometrie erzielt werden.Particularly advantageously, the dome-shaped bulge can be generated in the truss surface by being introduced by embossing in a flat truss surface. As a result, an advantageously cost-effective realization of the truss surface geometry can be achieved.
Bei einer besonders bevorzugten Ausgestaltung ist die kalottenförmige Ausbuchtung symmetrisch um eine die Traverse senkrecht zu ihrer Längsachse halbierende Achse angeordnet. Das bedeutet, die kalottenförmige Ausbuchtung ist vorteilhaft insgesamt symmetrisch auf der Seite der Traverse angeordnet, die in Kontakt kommt mit dem kalottenförmigen Endbereich der Stange. Dadurch kann vorteilhaft eine definierte Position eines Mittelpunktes der kalottenförmigen Ausbuchtung auf der Traverse erzeugt werden, was wiederum zu einer vorteilhaft definierten Führung der Stange durch die Traverse führt.In a particularly preferred embodiment, the dome-shaped indentation is arranged symmetrically about an axis which halves the cross-piece perpendicular to its longitudinal axis. This means that the dome-shaped bulge is advantageously arranged symmetrically overall on the side of the traverse, which comes into contact with the dome-shaped end region of the rod. As a result, a defined position of a center point of the dome-shaped bulge can advantageously be generated on the traverse, which in turn leads to an advantageously defined guidance of the rod by the traverse.
Besonders bevorzugt ist die Traverse radial zu der Stößelachse beweglich angeordnet, wobei die Traverse insbesondere ohne radiale Befestigung in den Stößel eingelegt ist. Dadurch können vorteilhaft die Koaxialfehler über die radial bewegliche Traverse kompensiert werden. Denn die Koaxialfehler stellen vorteilhaft nur einen sehr geringen Anteil an den Hebelarmen a1 und a2, es handelt sich vorzugsweise um einen statischen Positionsfehler der Kalottenform. Bei einer vorteilhaften radial zur Stößelachse beweglichen Traverse findet daher die Traverse vorzugsweise innerhalb der ersten Hübe der Stange ihre Position und kann somit den statischen Positionsfehler bevorzugt ausgleichen.Particularly preferably, the Traverse is arranged to be movable radially to the plunger axis, wherein the traverse is inserted in particular without radial attachment in the plunger. As a result, the coaxial errors can advantageously be compensated via the radially movable traverse. Because the coaxial errors are advantageous only a very small proportion of the lever arms a 1 and a 2 , it is preferably a static position error of the dome shape. In an advantageous movable radially to the ram traverse cross member therefore preferably finds the traverse within the first strokes of the rod their position and thus can preferably compensate for the static position error.
Vorteilhaft ist ein Ausbuchtungsradius der kalottenförmigen Ausbuchtung der Traverse größer als ein Stangenradius des kalottenförmigen Endbereichs der Stange. Dadurch ergibt sich der Vorteil, dass die Stange sich vorteilhaft in allen Betriebszuständen mit ihrem kalottenförmigen Endbereich sicher in der kalottenförmigen Ausbuchtung der Traverse befindet.Advantageously, a bulge radius of the dome-shaped bulge of the traverse is greater than a rod radius of the dome-shaped end region of the rod. This results in the advantage that the rod is advantageously located in all operating states with their dome-shaped end safely in the dome-shaped bulge of Traverse.
Es ist eine Stangenführung mit einer Stangenführungsachse vorgesehen, wobei ein Stangenendradius des kalottenförmigen Endbereichs der Stange kleiner als oder gleich groß wie ein an dem oberen Totpunkt der Stange vorherrschender Abstand von einer Tangente an einer Stangenkalottenoberfläche an der Stangenachse zu einem Schnittpunkt der Stößelachse und der Stangenführungsachse ist.There is provided a rod guide having a rod guide axis, wherein a rod end radius of the dome-shaped end portion of the rod is less than or equal to a distance at the top dead center of the rod from a tangent to a rod dome surface on the rod axis to an intersection of the ram axis and the rod guide axis ,
Der Abstand zwischen der Tangente an dem kalottenförmigen Endbereich der Stange in dem Punkt, in dem die Stangenachse eine Außenoberfläche der Stange schneidet, und einem Schnittpunkt der Stößelachse mit der Stangenführungsachse verändert sich während des Betriebes der Stange. Der Abstand ist im oberen Totpunkt der Stange kleiner als im unteren Totpunkt und sämtlichen Betriebszuständen dazwischen. Das bedeutet, der Radius des kalottenförmigen Endbereiches der Stange wird vorzugsweise kleiner bzw. gleich dem kleinsten Abstand zwischen dem Schnittpunkt der Führungsachsen und einer kleinsten Auskragung des Stangenendes - in der Position im oberen Totpunkt - gewählt. Dies führt dazu, dass die Aufstandswinkel β1 und β2 vorteilhaft kleiner bzw. gleich sind zum Winkelfehler α und dadurch vorzugsweise nur geringe Querkräfte wirken.The distance between the tangent to the dome-shaped end portion of the rod in the point where the rod axis intersects an outer surface of the rod and an intersection of the ram axis with the rod guide axis varies during operation of the rod. The distance is smaller at top dead center of the rod than at bottom dead center and all operating states in between. That is, the radius of the dome-shaped end portion of the rod is preferably less than or equal to the smallest distance between the intersection of the guide axes and a smallest protrusion of the rod end - in the position at top dead center - selected. This leads to the fact that the contact angle β 1 and β 2 are advantageously smaller or equal to the angular error α and thus preferably only small lateral forces act.
Die Druckbeeinflussungseinrichtung kann vorteilhaft eine Kraftstoffhochdruckpumpe sein, sie kann jedoch auch alternativ ein Motorventil sein.The pressure-influencing device may advantageously be a high-pressure fuel pump, but it may alternatively also be an engine valve.
Eine vorteilhafte Ausgestaltung der Erfindung wird nachfolgend anhand der beigefügten Zeichnungen näher erläutert.An advantageous embodiment of the invention will be explained in more detail with reference to the accompanying drawings.
Darin zeigt:
- Fig. 1
- einen Ausschnitt eines Verbrennungsmotors mit einer Druckbeeinflussungseinrichtung, wobei die Druckbeeinflussungseinrichtung eine Kraftstoffhochdruckpumpe ist, die mit einem Flansch in dem Verbrennungsmotor befestigt ist;
- Fig. 2
- einen Ausschnitt aus einem Verbrennungsmotor mit einer Druckbeeinflussungseinrichtung ohne Flanschbefestigung;
- Fig. 3
- die Druckbeeinflussungseinrichtung aus den
Fig. 1 undFig. 2 mit einer kalottenförmigen Ausbuchtung in einer Traverse eines Stößels; - Fig. 4
- die Druckbeeinflussungseinrichtung aus
Fig. 3 mit Winkelfehlstellungen; - Fig. 5
- die Druckbeeinflussungseinrichtung aus
Fig. 1 undFig. 2 , wobei die Traverse keine kalottenförmige Ausbuchtung aufweist; - Fig. 6
- die Druckbeeinflussungseinrichtung aus
Fig. 1 undFig. 2 mit kalottenförmiger Ausbuchtung in der Traverse; - Fig. 7
- eine schematische geometrische Darstellung der Druckbeeinflussungseinrichtung aus
Fig. 5 zur Darstellung der Aufstandswinkel und Hebelarme; - Fig. 8
- eine schematische geometrische Darstellung der Druckbeeinflussungseinrichtung aus
Fig. 6 zur Darstellung der vorherrschen Aufstandswinkel und Hebelarme; - Fig. 9
- eine schematische geometrische Darstellung der Druckbeeinflussungseinrichtung aus
Fig. 6 zur Darstellung idealer Radienverhältnisse der kalottenförmigen Ausbuchtung sowie eines kalottenförmigen Endbereiches einer Stange; - Fig. 10
- eine weitere schematische geoemtrische Darstellung der Druckbeeinflussungseinrichtung aus
Fig. 6 zur Darstellung idealer Radienverhältnisse der kalottenförmigen Ausbuchung und des kalottenförmigen Endbereiches; - Fig. 11
- ein Diagramm, das die in verschiedenen geometrischen Anordnungen der Druckbeeinflussungseinrichtung vorherrschenden radialen Kräfte abhängig von der auf eine Stangenachse wirkende Kraft darstellt;
- Fig. 12
- eine Druckbeeinflussungseinrichtung nach dem Stand der Technik ohne geometrische Fehler; und
- Fig. 13
- eine Druckbeeinflussungseinrichtung nach dem Stand der Technik mit geometrischen Fehlern.
- Fig. 1
- a section of an internal combustion engine with a pressure-influencing device, wherein the pressure-influencing means is a high-pressure fuel pump, which is fixed with a flange in the internal combustion engine;
- Fig. 2
- a detail of an internal combustion engine with a pressure influencing device without Flanschbefestigung;
- Fig. 3
- the pressure influencing device from the
Fig. 1 andFig. 2 with a dome-shaped bulge in a crosshead of a plunger; - Fig. 4
- the pressure influencing device
Fig. 3 with angular misalignments; - Fig. 5
- the pressure influencing device
Fig. 1 andFig. 2 , wherein the traverse has no dome-shaped bulge; - Fig. 6
- the pressure influencing device
Fig. 1 andFig. 2 with dome-shaped bulge in the traverse; - Fig. 7
- a schematic geometric representation of the pressure influencing device
Fig. 5 for displaying the contact angle and lever arms; - Fig. 8
- a schematic geometric representation of the pressure influencing device
Fig. 6 to show the prevailing contact angles and lever arms; - Fig. 9
- a schematic geometric representation of the pressure influencing device
Fig. 6 to illustrate ideal radii ratios of the dome-shaped bulge and a dome-shaped end portion of a rod; - Fig. 10
- a further schematic geoemtrical representation of the pressure influencing device
Fig. 6 to Representation of ideal radii ratios of the dome-shaped debit and the dome-shaped end region; - Fig. 11
- a diagram illustrating the prevailing radial forces in various geometric arrangements of the pressure influencing device depending on the force acting on a rod axis force;
- Fig. 12
- a pressure-influencing device according to the prior art without geometric errors; and
- Fig. 13
- a pressure-influencing device according to the prior art with geometric errors.
Im Folgenden stehen die Begriffe "Stange" und "Kolben" synonym füreinander. Gleiches gilt für die Begriffe "Druckbeeinflussungseinrichtung", "Motorventil" und "Kraftstoffhochdruckpumpe".In the following, the terms "rod" and "piston" are synonymous for each other. The same applies to the terms "pressure-influencing device", "engine valve" and "high-pressure fuel pump".
In
Die Rolle 38 und die Nockenwelle 65 bilden somit gemeinsam einen Stößelantrieb 66.The
In der idealisierten Darstellung in
Wie weiter in
Bei der idealen Ausführung der Druckbeinflussungseinrichtung 28 kontaktieren sich die Traverse 36 und die Stange 12 punktförmig in einem Kontaktbereich 68 einer Traversenoberfläche 70 und eines zweiten Endbereiches 42 der Stange 12, die einem ersten Endbereich 22 gegenüberliegt. In dem Kontaktbereich 68 weist die Traverse eine kalottenförmige Ausbuchtung 72 und die Stange 12 einen kalottenförmigen Endbereich 74 auf. Die kalottenförmige Ausbuchtung 72 überspannt nicht die gesamte Traversenoberfläche 70, sondern die Traverse 36 weist benachbart zu der kalottenförmigen Ausbuchtung 72 eine senkrecht zur Stößelachse 40 eben ausgebildete Traversenoberfläche auf. Die kalottenförmige Ausbuchtung 72 kann beispielsweise durch Prägen in die Traversenoberfläche 70 eingebracht werden. Die kalottenförmige Ausbuchtung 72 ist symmetrisch auf der Traversenoberfläche 70 angeordnet, so dass der niedrigste Punkt der kalottenförmigen Ausbuchtung 72 von der Stößelachse 40, die senkrecht zu einer Längsachse 76 der Traverse 36 verläuft, geschnitten wird.In the ideal embodiment of the
Dies zeigt ein Vergleich zwischen einer Druckbeeinflussungseinrichtung 28 gemäß dem Stand der Technik, gezeigt in
Wie in
Weiter entsteht durch die Verkippung der Stange 12 weg von der Stößelachse 40 der Winkelfehler α. Die Aufstandswinkel β1, β2 resultieren aus der Summe von α und γ.Next created by the tilting of the
Das bedeutet, dass der Winkelfehler γ in günstigen Situationen - im Folgenden bezeichnet als "best case" - den Winkelfehler α je nach Vorzeichen ausgleichen kann. Er kann den Winkelfehler α jedoch auch noch weiter verstärken, im Folgenden als "worst case" bezeichnet.This means that the angle error γ in favorable situations - hereinafter referred to as "best case" - can compensate the angle error α depending on the sign. However, it can also amplify the angle error α even further, referred to below as the "worst case".
Durch die Summe aus α und γ resultieren die in
Hier ist zu sehen, dass durch die kalottenförmige Ausbuchtung 72 in der Traverse 36 der Winkelfehler γ der Traverse 36 irrelevant wird. Das bedeutet, dass der Aufstandswinkel β nur so groß sein kann wie der Winkelfehler α. Es resultiert daher auch nur der Hebelarm a2, d.h. ein Abstand zwischen Kontaktpunkt K und Stangenachse 26, der Hebelarm a1 entfällt.Here it can be seen that the angle error γ of the
Dadurch ergeben sich insgesamt deutlich geringere Querkräfte, die auf die Druckbeeinflussungseinrichtung 28 wirken, was zu deutlich geringeren Belastungen und einem geringeren Verschleiß der Druckbeeinflussungseinrichtung 28 führt.As a result, overall significantly lower transverse forces, which act on the pressure-influencing
Es ist vorteilhaft, wenn die Hertz'schen Pressungen ohne Einschränkung der Herstellungstoleranzen konstant gehalten werden. Dies kann durch vorteilhafte Wahl der Radienverhältnisse von kalottenförmiger Ausbuchtung 72 und kalottenförmigem Endbereich 74 geschehen.It is advantageous if the Hertzian pressures are kept constant without limiting the manufacturing tolerances. This can be done by advantageous choice of the radii of dome-shaped
Dabei sind zwei Fälle zu unterscheiden. Unterscheidungskriterium ist dabei die Bedingung, dass die Hertz'sche Pressung im Vergleich zu einer Anordnung der Druckbeeinflussungseinrichtung 28, wie sie in
Im ersten Fall ist es möglich, den Stangenendradius 84 kleiner auszubilden als den Abstand amin, was in
Aufgrund zu groß werdender Hertz'scher Pressungen kann es jedoch auch ungünstig sein, den Stangenendradius 84 kleiner auszubilden als den Abstand amin. Diese Situation - zweiter Fall - ist in
In allen Betriebszuständen jedoch ist es vorteilhaft, wenn ein Ausbuchtungsradius 88 der kalottenförmigen Ausbuchtung 72 der Traverse 36 größer ist als der Stangenendradius 84.In all operating states, however, it is advantageous if a
Deshalb ist es weiter vorteilhaft, wenn für eine ausreichende Steifigkeit der Traverse 36 gesorgt wird. Dadurch kann erreicht werden, dass sich der Kontaktpunkt K immer zwischen den Achsen 50, 52 befindet und eine sehr geringe Streuung zwischen "worst case"- und "best case"-Toleranzen realisiert werden kann.Therefore, it is also advantageous if the
Wie zu sehen, ist in
Aufgrund der Hertz'schen Pressungen kann es jedoch auch günstig sein, wenn der Stangenendradius 84 größer gewählt ist als amin. Auch diese Konstellation stellt eine deutliche Verbesserung zur Situation in
Die Situation - Fall zwei - ist in
Dabei sind die Kräfte für vier verschiedene Anordnungen der druckbeeinflussenden Einrichtung 28 aufgetragen. Diagramm A stellt die Kräfteverhältnisse für eine Druckbeeinflussungseinrichtung 28 ohne kalottenförmige Ausbuchtung 72 in der Traverse 36 für die "best case"-Situation dar, die in
Das Diagramm C stellt dagegen die Situation für eine Druckbeinflussungseinrichtung 28 ohne kalottenförmige Ausbuchtung 72 für das "worst case"-Szenario - Aufstandspunkt 78 in
Das Diagramm B zeigt die Kräfteverhältnisse für eine Druckbeeinflussungseinrichtung 28, die eine kalottenförmige Ausbuchtung 72 in der Traverse 36 aufweist. Die Traverse 36 im Diagramm B weist eine radiale Beweglichkeit zur Stößelachse 40 auf.Diagram B shows the force relationships for a pressure-influencing
Das Diagramm D zeigt die Situation einer Druckbeeinflussungseinrichtung 28 mit der kalottenförmigen Ausbuchtung 72, wenn die Traverse 36 jedoch fixiert ist und nicht radial zur Stößelachse 40 beweglich ist.Diagram D shows the situation of a pressure-influencing
Es ist klar zu sehen, dass die Anordnung mit kalottenförmiger Ausbuchtung 72 und beweglicher Traverse 36 deutlich bessere Kräfteverhältnisse liefert, als das "worst case"-Szenario der Druckbeeinflussungseinrichtung 28 ohne kalottenförmige Ausbuchtung 72. Da das Erreichen von "worst case" und "best case" nicht steuerbar ist und der Kräfteverlauf im Diagramm B nahe an den "best case"-Fall herankommt, ergibt sich ein besser steuerbares Kräfteverhältnis in einer Druckbeeinflussungseinrichtung 28 mit kalottenförmiger Ausbuchtung 72. Gleichzeitig zeigen die Unterschiede der Diagramme B und D jedoch, dass eine radial bewegliche 36 deutlich begünstigt ist.It can be clearly seen that the arrangement with dome-shaped
Insgesamt erzeugt also die kalottenförmige Ausbuchtung 72 richtungsunabhängige Querkräfte, welche auf niedrigem Niveau zwischen "best case" und "worst case" der Druckbeeinflussungseinrichtung 28 nach dem Stand der Technik liegen. Dies entspricht einer allgemeinen Reduzierung der vorherrschenden Querkräfte.Overall, therefore, the dome-shaped
Insgesamt können die aus den Axialkräften Fa durch geometrische Ungänzen der Bauteile stammenden Querkräfte im Vergleich zu der "worst case"-Konstellation aus dem Stand der Technik um bis zu 40% reduziert werden. Die schädlichen Einflüsse der Querkräfte durch die Aufstandswinkel β1, β2 können größtenteils eliminiert werden, was zu einer Reduzierung der Querkräfte führt. Gleichzeitig ist die Rechtwinkligkeit der Traverse 36 zur Stößelachse 40 nahezu irrelevant, was zu einer Reduzierung der Herstellungskosten führt. Die kalottenförmige Ausbuchtung 72 der Traverse 36 kann durch einfaches Prägen erzeugt werden, was besonders kostengünstig ist. Insgesamt wird der Winkelfehler γ vollständig eliminiert und die Streuung und Größe des Gesamtwinkelfehlers β1 bzw. β2 wird erheblich reduziert, so dass für die Auslegung mit nahezu konstanten Belastungen gerechnet werden kann und "best case" bzw. "worst case" vorteilhaft nahe beieinander liegen. Zusätzlich können bei geschickter Paarung des Stangenradius 84 und des Ausbuchtungsradius 88 β1 bzw. β2 sogar kleiner als der unvermeidbare Winkelfehler α zwischen den Achsen 50, 52 der Führungen gehalten werden. Diese Vorteile können genutzt werden, um die Axiallast Fa insgesamt zu steigern, die Lebensdauer der Führungen 30, 32 zu verbessern, d.h. die Robustheit zu steigern, die erforderlichen Führungslängen zu reduzieren, was mit einer Kostensenkung und einer Bauraumverkleinerung einhergeht, und insgesamt die Toleranzen der Bauteile zu erweitern, was ebenfalls zu einer Kostensenkung im Herstellungsprozess beiträgt.Overall, the transverse forces resulting from the axial forces F a due to geometric discontinuities of the components can be reduced by up to 40% in comparison to the "worst case" constellation of the prior art. The harmful effects of the lateral forces by the contact angle β 1 , β 2 can be largely eliminated, resulting in a reduction of the lateral forces. At the same time, the perpendicularity of the
Alternativ zu der beschriebenen Anordnung kann die kalottenförmige Ausbuchtung 72 selbstverständlich auch in einem separaten Gleitschuh, der in dem Stößel 10 angeordnet ist, vorgesehen sein.As an alternative to the described arrangement, the dome-shaped
- 1010
- Stößeltappet
- 1212
- Stangepole
- 1414
- Kolbenpumpepiston pump
- 1616
- KraftstoffhochdruckpumpeHigh-pressure fuel pump
- 1818
- Motorventilengine valve
- 2020
- Kolbenpiston
- 2222
- erster Endbereichfirst end area
- 2424
- Kolbenachsepiston axis
- 2626
- Stangenachserod axis
- 2828
- DruckbeeinflussungseinrichtungPressure influencing device
- 3030
- Stangenführungrod guide
- 3232
- Stößelführungtappet guide
- 3434
- Stößelhemdtappet skirt
- 3636
- Traversetraverse
- 3838
- Rollerole
- 4040
- Stößelachseram axis
- 4242
- zweiter Endbereichsecond end area
- 4444
- Flanschflange
- 4646
- Kontaktpunktcontact point
- 4848
- Stangenenderod end
- 5050
- StößelführungsachseTappet guide axis
- 5252
- StangenführungsachseRod guide axis
- 5454
- Flanschflächeflange
- 5656
- Verbrennungsmotorinternal combustion engine
- 5858
- Flanschebeneflange plane
- 6060
- erster oberer Totpunktfirst top dead center
- 6262
- zweiter unterer Totpunktsecond bottom dead center
- 6565
- Nockenwellecamshaft
- 6666
- Stößelantriebram drive
- 6868
- Kontaktbereichcontact area
- 7070
- TraversenoberflächeTravers surface
- 7272
- kalottenförmige Ausbuchtungdome-shaped bulge
- 7474
- kalottenförmiger Endbereichdome-shaped end region
- 7676
- Längsachse TraverseLongitudinal axis traverse
- 7878
- Aufstandspunkt "worst case"Attack point "worst case"
- 8080
- Aufstandspunkt "neutral case"Contact point "neutral case"
- 8282
- Aufstandspunkt "best case"Attack point "best case"
- 8484
- StangenendradiusStangenendradius
- 8686
- StangenkalottenoberflächeStangenkalottenoberfläche
- 8888
- AusbuchtungsradiusAusbuchtungsradius
- 9090
- Hubstroke
- αα
- Winkelfehler (Stößelführungsachse - Stangenachse)Angle error (ram guide axis - rod axis)
- β1 β 1
- Aufstandswinkel (Stangenachse - Normale auf Traverse in Kontaktpunkt)Rise angle (rod axis - normal on traverse in contact point)
- β2 β 2
- Aufstandswinkel (Stößelführungsachse/Stößel - Normale auf Traverse zu Kontaktpunkt)Rise angle (ram guide axis / ram - normal on traverse to contact point)
- γγ
- Winkelfehler Traverse (Winkel Traverse zu Stößelführung)Angle error traverse (angle traverse to tappet guide)
- AA
- "best case" ohne kalottenförmige Ausbuchtung"best case" without dome-shaped bulge
- BB
- bewegliche Traverse mit kalottenförmiger Ausbuchtungmovable crossbar with dome-shaped bulge
- CC
- "worst case" ohne kalottenförmige Ausbuchtung"worst case" without dome-shaped bulge
- DD
- fixierte Traverse mit kalottenförmiger Ausbuchtungfixed traverse with dome-shaped bulge
- KK
- Kontaktpunkt Stange und TraverseContact point bar and traverse
- PP
- Pfeilarrow
- SS
- Schnittpunkt Stößelachse/StangenachseIntersection of plunger axis / rod axis
- TT
- Tangentetangent
- Fa F a
- Axiallast/Hertz'sche Pressung/AxialkraftAxial load / Hertzian pressure / axial force
- a1 a 1
- Abstand Kontaktpunkt zu Stößelführungsachse/ StößelachseDistance of contact point to ram guide axis / ram axis
- a2 a 2
- Abstand Kontaktpunkt zu Stangenführungsachse/ StangenachseDistance of contact point to rod guide axis / rod axis
- amin a min
- Abstand Tangente an Stangenkalottenoberfläche zu Schnittpunkt Stößelachse/StangenachseDistance between tangent to rod cap surface to intersection of plunger axis / rod axis
Claims (7)
- Pressure-influencing device (28) for influencing a pressure in a medium, having- a rod (12) with a first end region (22) for delimiting a space which has the medium, wherein the rod (12) is arranged so as to be movable along a rod axis (26) between a first, top dead center (60) and a second, bottom dead center (62);- a plunger (10) with a traverse (36) which is arranged substantially perpendicular to a plunger axis (40) and which serves for transmitting kinetic energy from a plunger drive (66) to the rod (12) in a contact region (68) between a traverse surface (70) and a second end region (42) of the rod (12), said second end region being arranged opposite the first end region (22),- wherein the rod (12) has, in the contact region (68), a calotte-shaped end region (74) and the traverse (36) has, in the contact region (68), a calotte-shaped recess (72), characterized in that a rod guide (30) having a rod guide axis (52) is provided, wherein a rod end radius (84) of the calotte-shaped end region (74) of the rod (12) is smaller than or equal to a spacing (amin), which exists at the top dead center (60) of the rod (12), between a tangent (T) to a rod calotte surface (86) at the rod axis (26) and an intersection point (S) of the plunger axis (40) and the rod guide axis (50).
- Pressure-influencing device (28) according to Claim 1, characterized in that the traverse (36) has, in regions adjoining the calotte-shaped recess (72), a traverse surface (70) which is of planar form substantially perpendicular to the plunger axis (40).
- Pressure-influencing device (28) according to Claim 1 or 2,
characterized in that the calotte-shaped recess (72) is formed into the traverse surface (70) by stamping. - Pressure-influencing device (28) according to one of Claims 1 to 3,
characterized in that the calotte-shaped recess (72) is arranged symmetrically about an axis which bisects the traverse (36) perpendicularly to the longitudinal axis (76) thereof. - Pressure-influencing device (28) according to one of Claims 1 to 4,
characterized in that the traverse (36) is arranged so as to be movable radially with respect to the plunger axis (40), wherein the traverse (36) is in particular inserted into the plunger (10) without radial fastenings. - Pressure-influencing device (28) according to one of Claims 1 to 5,
characterized in that a recess radius (88) of the calotte-shaped recess (72) of the traverse (36) is greater than a rod end radius (84) of the calotte-shaped end region (74) of the rod (12). - Pressure-influencing device (28) according to one of Claims 1 to 6,
characterized in that it is a high-pressure fuel pump (16) or an engine valve (18).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014216173.8A DE102014216173B4 (en) | 2014-08-14 | 2014-08-14 | High-pressure fuel pump and pressure-influencing device |
PCT/EP2015/064309 WO2016023665A1 (en) | 2014-08-14 | 2015-06-24 | High-pressure fuel pump and pressure control device |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3039281A1 EP3039281A1 (en) | 2016-07-06 |
EP3039281B1 true EP3039281B1 (en) | 2017-09-20 |
Family
ID=53498984
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15733402.0A Active EP3039281B1 (en) | 2014-08-14 | 2015-06-24 | High-pressure fuel pump or engine valve |
Country Status (7)
Country | Link |
---|---|
US (1) | US10294905B2 (en) |
EP (1) | EP3039281B1 (en) |
JP (1) | JP6218963B2 (en) |
KR (1) | KR101891012B1 (en) |
CN (1) | CN105745435B (en) |
DE (1) | DE102014216173B4 (en) |
WO (1) | WO2016023665A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014216173B4 (en) | 2014-08-14 | 2016-06-30 | Continental Automotive Gmbh | High-pressure fuel pump and pressure-influencing device |
JP7204561B2 (en) * | 2019-03-28 | 2023-01-16 | 本田技研工業株式会社 | Fuel pump |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3831457A (en) * | 1973-03-05 | 1974-08-27 | Gen Motors Corp | Variable tracking cam follower |
FR2356815A1 (en) * | 1976-07-02 | 1978-01-27 | Semt | DEVICE ALLOWING TO INJECT WATER INTO THE CYLINDERS OF AN INTERNAL COMBUSTION ENGINE, IN PARTICULAR TO REDUCE THE POLLUTION RATE OF THE LATTER |
DE2712450C2 (en) * | 1977-03-22 | 1984-08-23 | Klöckner-Humboldt-Deutz AG, 5000 Köln | Pump piston drive for a fuel injection pump for internal combustion engines |
DE8129048U1 (en) * | 1980-11-21 | 1982-03-18 | RIV-SKF Officine di Villar Perosa S.p.A., 10123 Torino | SELF-ADJUSTING HYDRAULIC PILOT FOR A THERMAL ENGINE VALVE CONTROL |
JPS59157047A (en) | 1983-02-28 | 1984-09-06 | Nippon Mining Co Ltd | Preparation of dehydromuscone |
DK0512138T3 (en) * | 1991-05-07 | 1994-09-26 | Hauhinco Maschf | High pressure pump for purified water |
JPH1030525A (en) * | 1996-07-16 | 1998-02-03 | Denso Corp | High pressure supply pump |
DE19802475A1 (en) * | 1998-01-23 | 1999-07-29 | Bosch Gmbh Robert | Radial piston pump to supply fuel at high pressure for fuel injection system of internal combustion engine |
JPH11343943A (en) | 1998-05-29 | 1999-12-14 | Denso Corp | Fuel injection pump |
JP3644279B2 (en) | 1998-12-11 | 2005-04-27 | 日産自動車株式会社 | Engine valve gear |
DE102004023541A1 (en) * | 2004-05-13 | 2005-12-01 | Robert Bosch Gmbh | High-pressure pump for a fuel injection device of an internal combustion engine |
WO2008068116A1 (en) * | 2006-12-05 | 2008-06-12 | Schaeffler Kg | Mechanical tappet, in particular for a fuel pump of an internal combustion engine |
US7793583B2 (en) | 2006-12-06 | 2010-09-14 | Schaeffler Kg | Mechanical tappet in particular for a fuel pump of an internal combustion engine |
JP4569563B2 (en) | 2006-12-07 | 2010-10-27 | 株式会社デンソー | Cam mechanism mounted device |
DE102007022220A1 (en) * | 2007-05-11 | 2008-11-13 | Robert Bosch Gmbh | High-pressure pump for combustion engine fuel system, has tappet floor and piston coupled via first and second coupling sections |
DE102007057911A1 (en) | 2007-12-01 | 2009-06-04 | Schaeffler Kg | Valve train unit for internal combustion engine, has bucket tappet and adjusting element comprising curved contact surfaces complementary to each other, where adjusting element freely movably lies against contact surfaces at tappet |
DE102008008438A1 (en) | 2008-02-11 | 2009-08-13 | Continental Automotive Gmbh | High-pressure pump has tappet, which serves for indirect support of piston with longitudinal axis at drive shaft over roller, which is pivotally coupled with tappet |
DE102013213419A1 (en) * | 2013-07-09 | 2015-01-15 | Robert Bosch Gmbh | New plunger tip geometry for a pressure control valve |
DE102014216173B4 (en) | 2014-08-14 | 2016-06-30 | Continental Automotive Gmbh | High-pressure fuel pump and pressure-influencing device |
-
2014
- 2014-08-14 DE DE102014216173.8A patent/DE102014216173B4/en active Active
-
2015
- 2015-06-24 EP EP15733402.0A patent/EP3039281B1/en active Active
- 2015-06-24 WO PCT/EP2015/064309 patent/WO2016023665A1/en active Application Filing
- 2015-06-24 CN CN201580002794.8A patent/CN105745435B/en active Active
- 2015-06-24 JP JP2016555927A patent/JP6218963B2/en active Active
- 2015-06-24 US US15/031,513 patent/US10294905B2/en active Active
- 2015-06-24 KR KR1020167017380A patent/KR101891012B1/en active IP Right Grant
Non-Patent Citations (1)
Title |
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None * |
Also Published As
Publication number | Publication date |
---|---|
WO2016023665A1 (en) | 2016-02-18 |
CN105745435A (en) | 2016-07-06 |
EP3039281A1 (en) | 2016-07-06 |
US10294905B2 (en) | 2019-05-21 |
DE102014216173B4 (en) | 2016-06-30 |
JP2017501339A (en) | 2017-01-12 |
CN105745435B (en) | 2018-04-27 |
US20170159628A1 (en) | 2017-06-08 |
DE102014216173A1 (en) | 2016-02-18 |
KR101891012B1 (en) | 2018-08-22 |
JP6218963B2 (en) | 2017-10-25 |
KR20160091420A (en) | 2016-08-02 |
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