EP3077656A1 - Pompe à carburant - Google Patents

Pompe à carburant

Info

Publication number
EP3077656A1
EP3077656A1 EP15754184.8A EP15754184A EP3077656A1 EP 3077656 A1 EP3077656 A1 EP 3077656A1 EP 15754184 A EP15754184 A EP 15754184A EP 3077656 A1 EP3077656 A1 EP 3077656A1
Authority
EP
European Patent Office
Prior art keywords
roller
piston
fuel pump
pump
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.)
Granted
Application number
EP15754184.8A
Other languages
German (de)
English (en)
Other versions
EP3077656B1 (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
Original Assignee
Continental Automotive GmbH
Priority date (The priority date 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 date listed.)
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
Anticipated expiration legal-status Critical

Links

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 to ⁇ least comprising: a pump piston, a cam shaft having at least one cam, a disposed between the pump piston and the cam roller plunger having a plunger body and a thereto rotatably supported roller, said pump piston and movements of the tappet body with respect to in parallel to the piston longitudinal center line directions terrorismsgekop ⁇ pelt, wherein the roller is in contact with the cam, wherein a geometric reference line, which extends the piston longitudinal ⁇ centerline rectilinear, the geometric axis of rotation of the roller intersects, and wherein said Plunger body has a parallel to the reference line ram body longitudinal centerline.
  • Such fuel pumps are used for example as force ⁇ high-pressure fuel pump 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.
  • Pressure phase is located at a suction phase in the so-called. Top dead center.
  • Radial piston pump is known per se, wherein in such known fuel pumps the
  • Plunger body longitudinal center line and the reference line lie on a common geometric straight lines.
  • 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 load acting on the roller in the contact zone line load is not always constant over the length of the contact zone in operation, but can, for example, due to low shape and / or
  • Position deviations regarding the center of the roll should be distributed unequally. Then results on the roll center, ie related to the position at the half roll length unbalanced Kraftein ⁇ line in the role. This can cause a torque about a torque axis perpendicular to the geometric axis of rotation of the roller.
  • an asymmetrical introduction of force via the roller contact in particular when rolling over top dead center, but also when rolling over bottom dead center, may under certain circumstances cause the tappet body to rotate about its tappet body longitudinal center line if no rotation lock is provided. Rotation of the plunger body may block and eventually destroy the pump drive.
  • the plunger body has a rectangular cross-section. It is also known that 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.
  • the invention has the object, advantageously further develop a fuel pump of the type mentioned.
  • the aim is a rotation of the tappet body in a simple and cheap way entge ⁇ genzu merge.
  • the object is achieved by the invention initially and essentially in conjunction with the features that the ram longitudinal body center line in a projection view oriented parallel to the geometric axis of rotation of the roller runs 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 pum ⁇ penkolben.
  • Tappet body longitudinal center line offset in said Russianionsbe ⁇ trachtung by a distance lateral to the running in the extension of the piston longitudinal centerline reference line acts by a frictional connection to the line of contact between roller and cam a, in particular to the line of contact of roller and cam parallel, opposing force that said with the Distance a gennavmoment forms. This counteracts an undesirable torque generated by an external asymmetrical introduction of force, as a result of which rotation of the tappet body can be prevented.
  • roller tappet from this desired rotational position prevents or at least made difficult.
  • 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, form ⁇ conclusive anti-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. At top dead center, the distance between the roller and the geometric axis of rotation of the camshaft is maximum. At bottom dead center, this distance is minimal.
  • the contact zone comprises the geometric contact line between the roller and the cam and in particular a narrow zone enclosing the geometric contact line
  • the so-called geometric reference line intersects the geometric axis of rotation of the camshaft.
  • 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 ram body longitudinal center line in the projection view is on that 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 reference line is made ⁇ continuously from the so-called lengthening the piston longitudinal center line, in other words, the tappet body longitudinal center line.
  • the tappet ⁇ body longitudinal center line is located in the projection view on the side of the reference line lying in terms of the contact portion of cam and roll selected for the operation of peripheral movement direction of the cam behind the reference line.
  • 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 tappet body is guided in to the tappet body longitudinal centerline pa ⁇ rallelen directions movable in a plunger guide body.
  • 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 smaller than that
  • Diameter of the outer envelope is.
  • 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 in a cylindrical manner. It is considered appropriate (i.e., not necessary) that the diameter of the inner envelope surface and the diameter of the outer envelope surface be matched to provide 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 Füh ⁇ tion surface can be generated by introducing a cylindrical bore in the plunger body.
  • the outwardly facing guide surface can be made on the plunger body by means of simple turning.
  • the piston longitudinal center line rectilinearly extending reference line and the plunger body longitudinal centerline lie in a common geometric plane, which extends perpendicular to the geometric axis of rotation of the camshaft he ⁇ .
  • 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 center line.
  • the outer Füh ⁇ approximately surface of the pump piston and the inner guide ⁇ surface of the pump piston guide along their respective entire circumference concentric and cylindrical about the piston benlteilsstoffline.
  • FIG. 1 schematically simplified in a longitudinal section components and their arrangement in a known fuel pump
  • FIG. 1a is a sectional view along section line 1a-1a according to FIG. 1 of a first known form-locking rotation lock for the tappet body
  • FIG. 1 is a sectional view along section line 1a-1a according to FIG. 1 of a first known form-locking rotation lock for the tappet body
  • FIG. 1b in a sectional view comparable to FIG. 1, la alternative second known form-locking Ver ⁇ rotation lock for the plunger body;
  • FIG. 2 shows a schematic longitudinal section of simplified components and their arrangement in a fuel pump according to the invention according to a preferred embodiment
  • FIG. 2a shows a sectional view along sectional plane IIa-IIa of Figure 2, with the omission of the compression spring and in Fig. 2a deviating scale.
  • FIG. 2b schematically and in comparison to FIG. 2a, in a somewhat different size, a plan view of the roller with a symmetrical line load acting on it at its dashed line of contact with the cam;
  • Fig. 2c schematically and in comparison to Fig. 2a in a slightly different size, a plan view of the roller with an indicated at its dashed line of contact with the cam acting on them unbalanced line load and
  • Fig. 2d is a schematic plan view of a longitudinal section of the roller with the roller in its rotational position stabilizing counterforce and the resulting counter torque.
  • 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 coupled to the pump piston 2' in a manner not shown in Figure 1, so that both components perform the same movements parallel to the piston longitudinal center line 10 '.
  • the plunger body 8 ' extends along a central plunger body longitudinal center line 13' that is central to it.
  • the plunger body longitudinal center line 13' on a geometric reference line 20 ' which extends the piston ⁇ longitudinal center line 10' in a straight line.
  • the piston longitudinal center line 10' and the plunger body longitudinal center line 13 'on a ge ⁇ common line extend the piston longitudinal center line 10' and the plunger body longitudinal center line 13 'on a ge ⁇ common line.
  • the plunger body 8 ' is in parallel to the plunger body longitudinal centerline 13' parallel directions, so in Figure 1 up and down, movably in a Stumbleel stresses- guide 14 'added. 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 circular, moreover, at its outer cross-sectional tappet body 8 ' has a radial projection 16' of '17 extending groove' with respect to the tappet body guide 14 'adopted in a parallel to the StumbleelSysteml Kunststoffsmit ⁇ telline 13 ,
  • the 18 'matching direction of rotation of the cam 6' is denoted by 19 '.
  • FIG. 1b shows a variant of FIG. 1a known in the prior art.
  • 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 a preferred exemplary embodiment of a fuel pump 1 according to the invention is schematically presented in simplified form.
  • the same reference numerals are selected for components that correspond to those of Figures 1 to lb, but omitted to distinguish the in Figures 1 to lb the numbers trailing stroke (') in Figures 2 to 2d.
  • 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, Be ⁇ part of the housing 15 of the fuel pump 1 or be firmly connected to the housing 15.
  • In the vicinity of the front end opens into the cylinder chamber 23 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 which leads, for example, to a (not shown in Figure 2 with Darge ⁇ set) high pressure accumulator an injection system for an internal combustion engine.
  • 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 shown in Figure 2, rotatably on it (ie, not rotatable relative to the shaft 5) mon ⁇ oriented cam 6.
  • 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 Figure 1 lower, a recess 30 for captive and thereby rotatable about its cross-sectional center or about its geometric axis of rotation 11 receiving the roller 9.
  • the recess 30 has to a radially inwardly facing bearing surface 31 which extends in the visible in Figure 1 cross-section along a circular contour, namely, to prevent falling out of the roller 9 down, 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 selected such that a small gap 32 shown in simplified form in FIG. 2 only results, into which fuel penetrates during operation and causes a lubrication or plain bearing of the roller 9, in particular hydrodynamic.
  • the roller tappet 7 is arranged between the pump piston 2 and the cam 6.
  • the roller shaft 7 is coupled in terms of movement to the pump piston 2, so that both components with respect to the two parallel to the piston longitudinal centerline 10 Rich ⁇ obligations run (back and forth) synchronous (insofar same) movements.
  • the pump piston is also in the sectional plane of Figure 2, but is shown without hatching. In the shown
  • the plunger body 8 is supported in the direction away from the cam 5, to the ram body longitudinal centerline parallel direction against a compression spring 33 from. 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.
  • the piston longitudinal center line 10 extends centrally through the pump piston 2.
  • the plunger body 8 extends along its central longitudinal ram body center line 13. It is movably received in a ram body guide 14 in directions parallel to the ram body longitudinal center line 13 ', ie upwards and downwards in FIG , This is only partially shown in Figure 2 and in the example also part of the housing 15 of the fuel pump 1, in which the cylinder chamber 23 is formed.
  • Figure 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 plunger longitudinal body line 13 and the reference line 20 are in a common, corresponding to the plane of Figure 2 and the geometric Rotary axis 38 of the camshaft 4 are perpendicular geo ⁇ metric plane (see Figure 2a). This corresponds to the desired unrotated alignment of the roller tappet 7.
  • the plane in which the ram body longitudinal center line 13 and the reference line 20 are also perpendicular to the geo ⁇ metric 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 is outside the perpendicular to the geometric axis of rotation 38 of the camshaft 4 and leading through the reference line 20 level.
  • the plunger body longitudinal center line 13 (different from the example shown in Figures 2 and 2a ) is outside the perpendicular to the geometric axis of rotation 38 of the camshaft 4 and leading through the reference line 20 level.
  • the projection view in turn is oriented so that the ram body longitudinal center line 13 extends at a lateral distance a from the geometric reference line 20.
  • the two lines 13 and 20 projected in a common viewing plane.
  • the ram body ⁇ longitudinal center line 13 in the projection view on that side of the reference line 20, with respect to the in the contact zone 37 of cam 6 and roller 9 for the operation selected circumferential movement direction (this is in Figure 2 at the same time indicated by the direction of rotation arrow 19) of the cam 6 in front of Be ⁇ zugsline 20 is located.
  • the plunger body 8 has on the outside a guide surface 41, which extends in total zy ⁇ lindrisch.
  • a guide surface 41 which extends in total zy ⁇ lindrisch.
  • 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 zy ⁇ - cylindrical guide surfaces, so that the pump piston 2 and the housing 15 is no positive connection in the direction of rotation about the piston longitudinal center line 10.
  • FIGS. 2 a and 2 b schematically illustrate by way of example two different distributions of the line load acting on the roller 9 in the contact zone to the cam 6 along the length of the contact zone 37. In the example of Figure 2b acts along the contact zone with respect to the roller center 39 of the roller 9 symmetrical line load 40.
  • the torque M12 could, without countermeasure in the upper and in the bottom dead center of the roller 9, cause an undesired rotation of the tappet body 8 about the tappet body longitudinal center line 13.
  • a rotation of the roller 9 oriented in the direction of the arrow by M 12 would however cause a counter-torque M 3 directed counter to the torque M 12.
  • the simplified graph in FIG. 2d shows that a counterforce F3 caused by the frictional connection at the line contact of the contact zone 37 acts with a lever arm of the length of the lateral spacing a about the ram longitudinal axis 13, resulting in the counter torque M3.

Landscapes

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

Abstract

L'invention concerne une pompe à carburant (1) comprenant au moins : un piston de pompe (2), un arbre à cames (4) qui comporte au moins une came (6), et un poussoir à galet agencé entre le piston de pompe (2) et la came (6) et comportant un corps de poussoir (8), sur lequel un galet (9) est maintenu de manière à pouvoir tourner. Le piston de pompe (2) et le corps de poussoir (8) sont solidaires en mouvement dans des directions parallèles à le ligne médiane longitudinale (10) du piston, le galet (9) se trouve en contact avec la came (6), une ligne géométrique de référence (20) qui prolonge en ligne droite la ligne médiane longitudinale (10) du piston coupe l'axe de rotation géométrique (11) du galet (9), et le corps de poussoir (8) présente une ligne médiane longitudinale (13) de corps de poussoir parallèle à la ligne de référence (20). Selon un perfectionnement avantageux la ligne médiane longitudinale (13) du corps de poussoir, vue en projection orientée parallèlement à l'axe de rotation (11) géométrique du galet (9), passe à une distance latérale (a) de la ligne de référence (20) géométrique.
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 true EP3077656A1 (fr) 2016-10-12
EP3077656B1 EP3077656B1 (fr) 2018-01-24

Family

ID=54007693

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15754184.8A Active EP3077656B1 (fr) 2014-10-14 2015-08-20 Pompe à carburant

Country Status (7)

Country Link
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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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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DE102007060772A1 (de) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
JP2009236041A (ja) 2008-03-27 2009-10-15 Toyota Motor Corp 燃料ポンプのローラリフタ構造
DE102008019072B3 (de) 2008-04-15 2009-12-31 Dionex Softron Gmbh Kurvengetriebe, insbesondere für eine Kolbenpumpe für die Hochleistungsflüssigkeitschromatographie
DE102008001718A1 (de) 2008-05-13 2009-11-19 Robert Bosch Gmbh Hochdruckkraftstoffpumpe
DE102009014833A1 (de) 2009-03-25 2010-09-30 Daimler Ag Antriebseinrichtung und Brennkraftmaschine
JP2010248974A (ja) 2009-04-14 2010-11-04 Toyota Motor Corp 高圧燃料ポンプ
DE102009028378A1 (de) 2009-08-10 2011-02-17 Robert Bosch Gmbh Hochdruckpumpe
JP5372692B2 (ja) 2009-10-06 2013-12-18 日立オートモティブシステムズ株式会社 高圧燃料ポンプ
DE102009047568A1 (de) 2009-12-07 2011-06-09 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102010027749A1 (de) 2010-04-14 2011-10-20 Robert Bosch Gmbh Hochdruckpumpe
JP5195893B2 (ja) * 2010-12-24 2013-05-15 トヨタ自動車株式会社 高圧ポンプ
JP5648620B2 (ja) 2011-11-02 2015-01-07 トヨタ自動車株式会社 高圧燃料ポンプ
EP2628942B1 (fr) * 2012-02-14 2014-10-01 Continental Automotive GmbH Pompe et système d'injection de carburant à rail commun
JP6102767B2 (ja) * 2014-01-24 2017-03-29 株式会社デンソー 高圧燃料ポンプ
DE102014220746B3 (de) 2014-10-14 2016-02-11 Continental Automotive Gmbh Kraftstoffpumpe

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US10054090B2 (en) 2018-08-21
KR101697770B1 (ko) 2017-01-18
KR20160107358A (ko) 2016-09-13
DE102014220746B3 (de) 2016-02-11
US20180171950A1 (en) 2018-06-21
WO2016058736A1 (fr) 2016-04-21
EP3077656B1 (fr) 2018-01-24
CN106062354B (zh) 2018-02-06
JP2017514053A (ja) 2017-06-01
JP6161833B2 (ja) 2017-07-12
CN106062354A (zh) 2016-10-26

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