EP3077656B1 - Pompe à carburant - Google Patents

Pompe à carburant Download PDF

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Publication number
EP3077656B1
EP3077656B1 EP15754184.8A EP15754184A EP3077656B1 EP 3077656 B1 EP3077656 B1 EP 3077656B1 EP 15754184 A EP15754184 A EP 15754184A EP 3077656 B1 EP3077656 B1 EP 3077656B1
Authority
EP
European Patent Office
Prior art keywords
roller
tappet body
fuel pump
piston
cam
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15754184.8A
Other languages
German (de)
English (en)
Other versions
EP3077656A1 (fr
Inventor
Thomas Schmidbauer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Continental Automotive GmbH
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Continental Automotive GmbH
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Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP3077656A1 publication Critical patent/EP3077656A1/fr
Application granted granted Critical
Publication of EP3077656B1 publication Critical patent/EP3077656B1/fr
Active legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2307/00—Preventing the rotation of tappets
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • 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
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8015—Provisions for assembly of fuel injection apparatus in a certain orientation, e.g. markings, notches or specially shaped sleeves other than a clip

Definitions

  • the present invention relates to a fuel pump, comprising at least: a pump piston, a camshaft having at least one cam, a roller tappet arranged between the pump piston and the cam, which has a tappet body and a roller rotatably supported thereon, wherein the pump piston and the tappet body with respect Movements are coupled in directions parallel to the piston longitudinal center line, wherein the roller is in contact with the cam, wherein a geometric reference line which extends the piston longitudinal center line rectilinearly intersects the geometric axis of rotation of the roller, and wherein the plunger body has a ram body longitudinal center line parallel to the reference line ,
  • Such fuel pumps are used, for example, as high-pressure fuel pumps for fuel injection systems of internal combustion engines.
  • the role of the roller tappet abuts the peripheral surface of the cam.
  • the plunger is movably received in its tappet body in directions parallel to the tappet body longitudinal centerline in a tappet body guide.
  • the roller tappet is reciprocated in directions opposite and parallel to its tappet body longitudinal centerline.
  • the geometric axis of rotation of the camshaft is the imaginary line around which the camshaft rotates exclusively.
  • the pump piston As long as during the rotation of the cam, the distance between the contact zone roller / cam and the geometric axis of rotation of the camshaft decreases, the pump piston, usually supported by a compression spring, during the so-called. Suction phase withdrawn from the pumping chamber, causing a so-called. Suction stroke executes. On the other hand, during the rotation of the cam, the distance between the contact zone roller / cam and the increased geometric axis of rotation of the camshaft, the pump piston is moved by means of the plunger body during the so-called. Pressure phase with its one longitudinal end first in the cylinder chamber of the pump piston into it, where he performs a so-called. Compression.
  • a line load which depends inter alia on the pressure force exerted by means of a supported against the housing of the fuel pump compression spring on the roller tappet.
  • the line load acting on the roller in the contact zone is not always constant over the length of the contact zone during operation, but may, for example, be unevenly distributed due to small form and / or positional deviations with respect to the center of the roller. Then results in the middle of the roll, ie the position at half the roll length related unbalanced force introduction into the role. This can cause a torque about a torque axis perpendicular to the geometric axis of rotation of the roller.
  • the plunger body has a round basic shape in cross-section, but at the outer edge of a radial projection is formed which forms a positive rotation with a recess in the housing-fixed plunger body guide. Again, this is considered to be disadvantageous in terms of design effort and cost.
  • JP 2013 096328 A discloses a fuel pump including a pump piston, a camshaft having a cam and an intermediate pumping piston, and cam-mounted roller tappets having a tappet body and a roller rotatably supported therein.
  • the pump piston and the plunger body are motion-coupled with respect to movements in a direction parallel to a piston longitudinal centerline.
  • the roller is in contact with the cams, with a geometric reference line that extends the piston longitudinal centerline in a straight line intersecting a geometric axis of rotation of the roller.
  • the invention has the object, advantageously further develop a fuel pump of the type mentioned.
  • it is desirable to counteract a rotation of the plunger body in a simple and inexpensive manner.
  • the object is achieved by the invention initially and essentially in conjunction with the features that the ram body longitudinal center line in a projection oriented parallel to the geometric axis of rotation of the roller projection view at a lateral distance from the geometric reference line.
  • the invention proposes to offset in contrast to the prior art, the plunger body longitudinal center line and thus the, preferably circular, cross-sectional outer contour of the plunger body in or against the direction of rotation of the cam or the drive shaft (in the direction perpendicular to the reference line).
  • neither the roller nor the camshaft are added to the pump piston.
  • the desired rotational position of the plunger body in which the geometric axis of rotation of the roller and the geometric axis of rotation of the cam shaft parallel to each other, stabilized.
  • rotation of the roller tappet from this desired rotational position can be prevented or at least made more difficult during operation in the upper and lower dead center of the roller.
  • the invention is based on the fundamentally novel idea to replace the known positive rotation of the plunger body by a non-positive rotation.
  • the invention advantageously makes it possible that manufacturing tolerances need not be unnecessarily restricted. Another advantage is seen in the fact that the cost of a geometric, positive rotation on the roller tappet can be omitted.
  • a cylindrical bore is sufficient as a longitudinal guide for the tappet body without additional, elaborate groove or other devices. It has also been found that the desired rotational position of the tappet body is stabilized in positions of the roller between the two dead centers by then acting on the roller at the contact zone to the cam a also directed transversely to the contact normal direction of line load.
  • the contact zone between the cam and roller is laterally spaced from the ram body longitudinal centerline.
  • the contact zone comprises the geometric contact line between the roller and the cam and in particular a narrow zone of Hertzian pressure enclosing the geometric contact line.
  • the so-called geometric reference line intersects the geometric axis of rotation of the camshaft. Appropriately (that is not necessary), the geometric axis of rotation of the roller is perpendicular to the reference line.
  • the geometric axis of rotation of the camshaft is perpendicular to the reference line.
  • the pump piston and the plunger body can be coupled in any desired manner, in particular by means of additional components of the fuel pump, in the directions parallel to the piston longitudinal center line and opposite to each other. As a result of the movement coupling, the pump piston and the tappet body execute synchronous movements parallel to the piston longitudinal center line.
  • the slide body longitudinal center line in the projection view is on the side of the reference line which is in front of the reference line with respect to the circumferential direction of movement of the cam selected in the contact area of cam and roller for operation.
  • the ram body longitudinal center line starting from the reference line extending the piston longitudinal center line, is offset laterally against the direction of rotation of the roller and cam relative to its contact area.
  • the ram body longitudinal centerline may be on the side of the datum line that is behind the datum line with respect to the circumferential direction of travel of the cam selected in the contact area of the cam and roller for operation.
  • the fuel pump comprises a cylinder space into which the pump piston projects and relative to which the pump piston can be reciprocated in a direction parallel to the piston longitudinal center line when the camshaft is rotated by means of the roller tappet.
  • the pump piston in the cylinder chamber in this Directions is longitudinally displaceable.
  • the plunger body is movably guided in directions parallel to the plunger body longitudinal center line in a plunger body guide.
  • a guide surface formed on the plunger it is considered to be advantageous for a guide surface formed on the plunger to lie on or radially within an inner cylindrical envelope surface, that a guide surface of the plunger body guide formed in a recess of the plunger body guide lies on or radially outside an outer cylindrical envelope surface and that the diameter of the inner envelope surface is smaller than the diameter of the outer envelope surface.
  • the cylindrical envelope surface of the guide surface of the ram is concentric with the ram body longitudinal centerline. It is preferred that the guide surface of the tappet body and / or that the guide surface of the tappet body guide extend at least in sections or as a whole cylindrically. As appropriate (ie, as not necessary), it is considered that the diameter of the inner envelope surface and the diameter of the outer envelope surface are matched to achieve a clearance fit or a transition fit between the tappet body and the tappet guide.
  • the outer guide surface of the plunger and the inner guide surface of the plunger body guide each extend continuously cylindrical along its entire circumference around the plunger body longitudinal centerline. This allows a particularly simple production.
  • the inwardly facing guide surface can be created by inserting a cylindrical bore in the plunger body.
  • the outwardly facing guide surface can be made on the plunger body by means of simple turning.
  • piston longitudinal center line rectilinearly extending reference line and the plunger body longitudinal centerline lie in a common geometric plane that extends perpendicular to the geometric axis of rotation of the camshaft.
  • the plunger body is supported by a compression spring against the housing of the fuel pump adjacent to a cylinder space cooperating with the pump piston and the pump piston in leading away from the cylinder chamber, is supported parallel to the piston longitudinal center line direction against the plunger body.
  • the fuel pump is a high-pressure fuel pump that is suitable and in particular adapted for this, fuel at a pressure of more than 100 bar, in particular at a pressure between 150 and 250 bar, or at a pressure of more than 1000 bar, in particular to compress pressure between 1500 and 2500 bar.
  • it may be a gasoline injection pump or a diesel injection pump for the engine of a motor vehicle. It is understood, however, that fuel pumps according to the invention can also be used for other purposes.
  • the pump piston has an outer guide surface which forms a longitudinal guide with an inner guide surface of a pump piston guide in the direction of the piston longitudinal centerline.
  • the outer guide surface of the pump piston and the inner guide surface of the pump piston guide extend concentrically and cylindrically about the piston longitudinal centerline along their respective entire circumference.
  • the fuel pump 1 comprises a pump piston 2', whose longitudinal direction in the direction of the upper end 3 ' a cylinder room protrudes.
  • the roller tappet 7 ' is arranged between the pump piston 2' and the cam 6 '.
  • the roller tappet 7 ' is connected to the pump piston 2' on in FIG. 1 not shown manner coupled so that both components parallel to the piston longitudinal centerline 10 'perform the same movements.
  • the roller 9 ' rolls on an outer edge 12' of the cam 6 'from.
  • the plunger body 8 ' extends along a central plunger body longitudinal center line 13' that is central to it.
  • the plunger body longitudinal centerline 13' is located on a geometric reference line 20 'which extends the piston longitudinal centerline 10' in a straight line.
  • the plunger body 8 ' is in parallel to the plunger body longitudinal centerline 13' parallel directions, ie in FIG. 1 up and down, movably received in a tappet body guide 14 '. This may be part of a housing 15 'of the fuel pump 1'.
  • the plunger body 8 'and the plunger body guide 14' together form a positive rotation about the ram body longitudinal centerline 13 'from.
  • the plunger body 8 ' which otherwise has a radial projection 16' on its outer cross-section, extends into a groove 17 'in the plunger body guide 14' extending parallel to the plunger body longitudinal center line 13 'with respect to the assumed direction of rotation of the roller 9', designated by 18 '. rotationally locking engages.
  • the 18 'matching direction of rotation of the cam 6' is denoted by 19 '.
  • FIG. 1b shows a known in the prior art variant FIG.
  • a Positive rotation is formed there by the fact that in the plunger body guide 14 'radially inwardly projecting pin 21' in a parallel to the longitudinal direction Plunger body longitudinal line 13 'extending groove 22' in the plunger body 8 'protrudes.
  • FIGS. 2 to 2d is schematically simplified a preferred embodiment of a fuel pump 1 according to the invention presented.
  • FIGS. 1 to 1b numerically the same reference numerals are chosen, but in order to distinguish the in the FIGS. 1 to 1b the numbers trailing the numbers (') in the FIGS. 2 to 2d eliminated.
  • the fuel pump 1 comprises a pump piston 2, the upper end 3 of which projects in the direction of the direction into a cylinder space 23.
  • the boundary wall 24 of the cylinder chamber 23 may be, for example, part of the housing 15 of the fuel pump 1 or be firmly connected to the housing 15.
  • a fluidically connected to a fuel tank 25 inlet line 26 for fuel in which an intake valve 27 is arranged as an inlet valve. This is open when the pressure in the cylinder chamber 23 during the suction phases, the pressure in the fuel tank 25 by a certain pressure difference below.
  • an outlet 28 of which, for example, to a (in FIG. 2 not shown) high-pressure accumulator an injection system for an internal combustion engine leads.
  • a pressure valve 29 is arranged as an outlet valve. This is open during pressure phases when the fuel pressure in the cylinder chamber 23 exceeds a certain pressure.
  • the fuel pump has a camshaft 4, which has a central shaft 5 and at least the one, in FIG. 2 shown, rotatably on it (ie, not rotatable relative to the shaft 5) mounted cam 6 has.
  • the fuel pump 1 comprises a roller tappet 7. This has a plunger body 8 and a manner not shown in detail about a central geometric (ie imaginary linear) axis of rotation 11 rotatably held roller 9.
  • the plunger body 8 has on its side facing away from the pump piston 2, that is in the view of FIG. 1 lower, side a recess 30 for captive and thereby about its cross-sectional center or about its geometric axis of rotation 11 rotatable recording of the roller 9.
  • the recess 30 has a radially inwardly facing bearing surface 31, which in the in FIG. 1 visible cross section along a circular contour, namely, to prevent falling out of the roller 9 down, extends along a circumferential angle of more than 180 degrees.
  • the diameter of said circular contour is slightly larger than the outer diameter of the roller 9, so that the roller 9 is rotatably supported.
  • the diameters are chosen so that a lower, in FIG. 2 simplified only shown as a simple line gap 32 results, penetrates into the fuel during operation and one, in particular hydrodynamic, lubrication or sliding bearing of the roller 9 causes.
  • the roller tappet 7 is arranged between the pump piston 2 and the cam 6.
  • the roller tappet 7 is rotationally coupled to the pump piston 2 so that both components perform synchronous (thus, equal) movements with respect to the two directions (back and forth) parallel to the piston longitudinal centerline 10.
  • the pump piston is also in the cutting plane of FIG. 2 , but is shown without hatching.
  • the plunger body 8 is supported against a compression spring 33 in the direction parallel to the plunger body longitudinal center line away from the cam 5. This is supported in the same direction against the cylinder chamber 23 adjacent housing 15 of the fuel pump 1.
  • the compression spring 33 is dimensioned so that it is in any possible position of the plunger body 8 under a spring pressure force and thus pushes the plunger body 8 in the direction of the cam 6.
  • the plunger body 8 is supported by means of a spring plate 34 on the compression spring 33.
  • the spring plate 34 is disposed between the compression spring 33 and a front bottom of a bore 35 formed in the plunger body 8. He engages with the inner edge of its central opening axially positive fit in a groove 36 in the pump piston 2, so that a positive connection results for both mutually opposite, parallel to a piston longitudinal center line 10 axial directions.
  • the roller 9 rolls on an outer edge 12 of the cam 6 from.
  • the piston longitudinal center line 10 extends centrally through the pump piston 2.
  • the plunger body 8 extends along its central longitudinal body center line 13 plunger body. He is in parallel to the ram body longitudinal centerline 13 'parallel directions, ie in FIG. 2 up and down, movably received in a tappet body guide 14. This is in FIG. 2 shown only partially and in the example also part of the housing 15 of the fuel pump 1, in which the cylinder chamber 23 is formed.
  • FIG. 2 shows a geometric or imaginary reference line 20, which extends the piston longitudinal center line 10 in a straight line to the cam 6 and which intersects the geometric axis of rotation 11 of the roller 9.
  • the reference line 20 also intersects the geometric axis of rotation 38 of the cam 6.
  • the drawing plane of FIG. 2 corresponding and perpendicular to the geometric axis of rotation 38 of the camshaft 4 geometric plane lie (see. FIG. 2a ). This corresponds to the desired non-rotated orientation of the roller tappet 7.
  • the plane in which the ram body longitudinal center line 13 and the reference line 20 lie, is also perpendicular to the geometric axis of rotation 11 of the roller. 9
  • the plunger body longitudinal center line 13 at a lateral distance a from the geometric reference line 20.
  • the plunger body longitudinal center line thirteenth (deviating from the one in FIG. 2 and 2a shown example) is outside of the geometric axis of rotation 38 of the camshaft 4 perpendicular and leading through the reference line 20 level.
  • the plunger body 8 on the outside has a guide surface 41, which extends generally cylindrical.
  • a bore 43 whose radially inwardly facing surface forms a guide surface 42 of the tappet body guide 14.
  • the guide surface 42 is also generally cylindrical. Consequently, the plunger body 8 and the plunger body guide 14 do not form a positive connection with each other in the rotational direction about the plunger body longitudinal center line 13.
  • the pump piston 2 and formed to its longitudinally displaceable guide in the housing 15 pump piston guide (in the example is the wall of the cylinder chamber 23) each have cylindrical guide surfaces, so that the pump piston 2 and the housing 15 no positive connection in the direction of rotation around the piston longitudinal centerline 10.
  • FIGS. 2b and 2c show schematically and in comparison to Fig. 2a in a slightly different size, a respective plan view of the roller 9, in an imaginary operating condition, in which the Roller 9 abuts against the cam 6 in the edge region of its greatest eccentricity with respect to the geometric axis of rotation 38 of the camshaft 4. This situation is also called top dead center.
  • the FIGS. 2a and 2b indicate schematically comparative exemplary two different distributions of the force acting on the roller 9 in the contact zone to the cam 6 line load along the length of the contact zone 37 at. In the example of FIG. 2b acts along the contact zone with respect to the roller center 39 of the roller 9 symmetrical line load 40.
  • FIG. 2d shows, according to the lateral distance a between the reference line 20 and the plunger body longitudinal center line 13 in the fuel pump 1 according to the invention an oriented in the arrow direction of M12 rotation of the roller 9 but cause a counter to the torque M12 counter torque M3.
  • the simplified graphic in Figure 2d shows that in this case a caused by the frictional connection at the line contact of the contact zone 37 counterforce F3 acts with a lever arm of the length of the lateral distance a to the ram, compassionlticiansstoffline 13, whereby the counter torque M3 results. This acts in opposite to the torque M12 rotation about the ram body longitudinal center line 13, so that both torques proportionately or even completely compensate, whereby the roller 9 and the plunger body.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Gears, Cams (AREA)

Claims (10)

  1. Pompe à carburant (1), comprenant au moins: un piston de pompe (2), un arbre à cames (4), qui présente au moins une came (6), un poussoir à galet (7) disposé entre le piston de pompe (2) et la came (6), qui présente un corps de poussoir (8) et un galet (9) maintenu de façon rotative sur celui-ci, dans laquelle le piston de pompe (2) et le corps de poussoir (8) sont cinématiquement couplés en ce qui concerne des mouvements dans des directions parallèles à la ligne centrale longitudinale du piston (10), dans laquelle le galet (9) se trouve en contact avec la came (6), dans laquelle une ligne de référence géométrique (20), qui prolonge en ligne droite la ligne centrale longitudinale de piston (10), coupe l'axe de rotation géométrique (11) du galet (9), et dans laquelle le corps de poussoir (8) possède une ligne centrale longitudinale de corps de poussoir (13) parallèle à la ligne de référence (20), caractérisée en ce que la ligne centrale longitudinale de corps de poussoir (13) s'étend, dans une vue en projection orientée parallèlement à l'axe de rotation géométrique (11) du galet (9), à une distance latérale (a) de la ligne de référence géométrique (20).
  2. Pompe à carburant (1) selon la revendication 1, caractérisée en ce que, au moins au point mort haut et en particulier au point mort bas du galet (9) dans la vue en projection, la zone de contact (37) entre la came (6) et le galet (9) est espacée latéralement de la ligne centrale longitudinale de corps de poussoir (13).
  3. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la ligne de référence géométrique (20) coupe l'axe de rotation géométrique (38) de l'arbre à cames (4).
  4. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la ligne centrale longitudinale de corps de poussoir (13) se situe, dans la vue en projection, sur le côté de la ligne de référence (20), qui est situé avant la ligne de référence (20) par rapport à la direction de mouvement périphérique de la came (6) choisie pour le fonctionnement dans la zone de contact de la came (6) et du galet (9), ou qui est situé après la ligne de référence (20) par rapport à la direction de mouvement périphérique de la came (6) choisie pour le fonctionnement dans la zone de contact de la came (6) et du galet (9).
  5. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que le corps de poussoir (8) est guidé dans un guide de corps de poussoir (14) de façon mobile dans des directions parallèles à la ligne centrale longitudinale de corps de poussoir (13), en ce qu'une surface de guidage (41) du corps de poussoir (8) se situe sur ou à l'intérieur d'une face d'enveloppe cylindrique intérieure, en ce qu'une surface de guidage (42) du guide de corps de poussoir (14) se situe sur ou à l'extérieur d'une face d'enveloppe cylindrique extérieure, et en ce que le diamètre de la face d'enveloppe intérieure est plus petit que le diamètre de la face d'enveloppe extérieure.
  6. Pompe à carburant (1) selon la revendication 5, caractérisée en ce que la surface de guidage extérieure (41) du corps de poussoir (8) et la surface de guidage intérieure (42) du guide de corps de poussoir (14) s'étendent le long de toute leur périphérie respective, chacune de façon cylindrique continue, autour de la ligne centrale longitudinale de corps de poussoir (13).
  7. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la ligne de référence (20) et la ligne centrale longitudinale de corps de poussoir (13) sont situées dans un plan géométrique qui leur est commun, qui s'étend perpendiculairement à l'axe de rotation géométrique (38) de l'arbre à cames (4).
  8. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que le corps de poussoir (8) est appuyé au moyen d'un ressort de pression (33) contre la région du carter (15) de la pompe à carburant (1) proche d'une chambre de cylindre (23) qui coopère avec le piston de pompe (2), et/ou en ce que le piston de pompe (2) est appuyé contre le corps de poussoir (8) dans une direction parallèle à la ligne centrale longitudinale de piston (10) s'éloignant de la chambre de cylindre (23).
  9. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que la pompe à carburant (1) est une pompe à carburant haute pression, qui est conçue et qui est en particulier adaptée pour comprimer du carburant à une pression de plus de 100 bars, en particulier à une pression comprise entre 150 et 250 bars, ou à une pression de plus de 1000 bars, en particulier à une pression comprise entre 1500 et 2500 bars.
  10. Pompe à carburant (1) selon l'une quelconque des revendications précédentes, caractérisée en ce que le piston de pompe (2) présente une surface de guidage extérieure, qui forme avec une surface de guidage intérieure d'un guide de piston de pompe un guidage longitudinal dans la direction de la ligne centrale longitudinale de piston (10), et en ce que la surface de guidage extérieure du piston de pompe (2) et la surface de guidage intérieure du guide de piston de pompe s'étendent le long de toute leur périphérie respective de façon concentrique et cylindrique autour de la ligne centrale longitudinale de piston (10).
EP15754184.8A 2014-10-14 2015-08-20 Pompe à carburant Active EP3077656B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014220746.0A DE102014220746B3 (de) 2014-10-14 2014-10-14 Kraftstoffpumpe
PCT/EP2015/069167 WO2016058736A1 (fr) 2014-10-14 2015-08-20 Pompe à carburant

Publications (2)

Publication Number Publication Date
EP3077656A1 EP3077656A1 (fr) 2016-10-12
EP3077656B1 true EP3077656B1 (fr) 2018-01-24

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EP15754184.8A Active EP3077656B1 (fr) 2014-10-14 2015-08-20 Pompe à carburant

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US (1) US10054090B2 (fr)
EP (1) EP3077656B1 (fr)
JP (1) JP6161833B2 (fr)
KR (1) KR101697770B1 (fr)
CN (1) CN106062354B (fr)
DE (1) DE102014220746B3 (fr)
WO (1) WO2016058736A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014220746B3 (de) 2014-10-14 2016-02-11 Continental Automotive Gmbh Kraftstoffpumpe
JP7120081B2 (ja) * 2019-03-01 2022-08-17 株式会社デンソー 燃料噴射ポンプ
CN114263585B (zh) * 2021-12-16 2024-07-09 北京空天技术研究所 一种活塞泵

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Also Published As

Publication number Publication date
US20180171950A1 (en) 2018-06-21
EP3077656A1 (fr) 2016-10-12
DE102014220746B3 (de) 2016-02-11
JP6161833B2 (ja) 2017-07-12
JP2017514053A (ja) 2017-06-01
US10054090B2 (en) 2018-08-21
CN106062354A (zh) 2016-10-26
WO2016058736A1 (fr) 2016-04-21
KR20160107358A (ko) 2016-09-13
KR101697770B1 (ko) 2017-01-18
CN106062354B (zh) 2018-02-06

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