WO2020064064A1 - Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile - Google Patents

Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile Download PDF

Info

Publication number
WO2020064064A1
WO2020064064A1 PCT/DE2019/200101 DE2019200101W WO2020064064A1 WO 2020064064 A1 WO2020064064 A1 WO 2020064064A1 DE 2019200101 W DE2019200101 W DE 2019200101W WO 2020064064 A1 WO2020064064 A1 WO 2020064064A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston
section
recess
cross
sectional area
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.)
Ceased
Application number
PCT/DE2019/200101
Other languages
German (de)
English (en)
Inventor
Yury Mikhaylov
Mykhailo Belikovetsky
Yavuz Kurt
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.)
Aumovio Germany GmbH
Original Assignee
Continental Automotive Technologies 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 Technologies GmbH filed Critical Continental Automotive Technologies GmbH
Publication of WO2020064064A1 publication Critical patent/WO2020064064A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/442—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 means preventing fuel leakage around pump plunger, e.g. fluid barriers

Definitions

  • the present invention relates to a device for loading a fluid feed pump for a motor vehicle, which enables reliable and safe operation of the fluid feed pump and can also contribute to an extended service life of the fluid feed pump.
  • the invention further relates to a fluid feed pump for a motor vehicle with such a device.
  • Motor vehicles with an internal combustion engine have a fluid feed pump which is coupled to the internal combustion engine and, for example as a gasoline or diesel high-pressure pump, delivers fuel to a high-pressure accumulator via one or more pistons moving up and down and makes it available for the internal combustion engine.
  • the fluid is usually provided with a fluid pressure of several hundred bar, so that safe and reliable operation of the fluid feed pump is necessary. In addition, it is always a matter of concern to improve the service life of such components and to enable inexpensive production.
  • the task is solved by the features of the independent patent claim. Advantageous refinements are specified in the subclaims.
  • a device for operating a fluid delivery pump for a motor vehicle comprises a piston element with a first piston section and at least one further piston section, which extend in an elongated manner with respect to a longitudinal axis of the piston element and are coupled to one another.
  • the device further comprises a piston recess which is formed on a wall of the piston element between the first piston section and the further piston section.
  • the piston element has a first cross-sectional area with respect to the longitudinal axis in the first piston section and a minimal cross-sectional area in the region of the piston recess and is designed such that the ratio of the minimum cross-sectional area and the first cross-sectional area is less than 0.75.
  • the piston element essentially implements a single-stage or multi-stage piston, at which the piston recess with a predetermined depth and a specific geometry is introduced at a specific position.
  • the piston recess can also be referred to as a groove.
  • Such a groove realizes the function of a hinge and provides a certain elasticity and flexibility of the piston element, which can have an advantageous effect on the operation in a fluid feed pump.
  • the cross section or the cross sectional area of the piston element can change over the area of the piston recess.
  • the minimum cross-sectional area in the region of the piston recess designates the smallest cross-sectional area which is related to the first cross-sectional area of the first piston section.
  • the cross-sectional ratio of the minimum cross-sectional area of the piston recess and the first cross-sectional area of the first piston section is less than 0.75.
  • the cross-sectional ratio described is less than 0.7 or 0.6 or 0, 5 or 0.4.
  • the piston recess is specifically designed to be so large that it has an influence on the elasticity and flexibility of the piston element, and not only takes on a lubricating or cooling function, but also influences and moves the piston element within a piston guide contributes to an advantageous function of the fluid feed pump.
  • the piston element Due to the groove or the piston recess, the piston element is more flexible in its upward and downward movement, so that the influence of transverse forces acting on the piston element is counteracted.
  • the lower part of the Kol benelements can therefore be deflected somewhat more, while the upper part is deflected less. A transverse force acting on the piston element is thereby distributed over a larger area of the piston element.
  • terms such as “above” or “below” designate a direction in relation to an operational state of the device in a fluid feed pump.
  • the fluid feed pump can in particular be a gasoline or high-pressure diesel pump which delivers the respective fuel into a high-pressure chamber or a high-pressure accumulator and with a fluid pressure of, for example, 300-400 bar or more for a combustion cycle in an internal combustion engine.
  • the piston element performs several functions.
  • the upper part of the piston element corresponds to the first piston section, for example, and forms the
  • the stroke volume of the high-pressure pump results from the diameter of the upper part of the piston element and the stroke of the piston element.
  • the maximum load on a roller tappet, which couples the lower part of the piston element to a camshaft, results from the diameter itself and the pressure in the high-pressure chamber and other forces, such as the elastic force of a piston return spring.
  • the lower part of the piston corresponds, for example, to the further piston section and forms an interface to the drive area.
  • This additional piston section is located, for example, partly on the fuel side within the fluid delivery pump and partly on the oil side of the internal combustion engine, for example in a cylinder head of the internal combustion engine.
  • a seal between the fuel and oil side is done, for example, via a rod seal in the fluid feed pump.
  • a piston return spring is supported, among other things, on a spring plate, which can be mounted on the lower part of the piston element.
  • the piston element is guided, for example, directly in a pump housing or in a separate component, such as a sleeve-shaped piston guide, and experiences a change in the lower part due to various influences, for example, due to the piston return spring, the rod seal, angularity and evenness of the roller tappet resulting shear force.
  • Such a transverse force usually acts at two points at which a piston is supported within a piston guide, and leads to a local load between the piston and piston guide. If this load is too high, this can lead to high wear, damage or even failure of the fluid feed pump.
  • An increase in the guide length of the piston guide and correspondingly longer pistons could be one
  • an existing high surface pressure between the piston and piston guide requires a correspondingly high hardness of the material of the components in order to ensure a certain service life.
  • transverse forces acting on the piston element can be usefully compensated for during operation of the fluid feed pump and can thus be reduced after partial effects on the material, the function and the required installation space of the interacting components.
  • the described device enables safe and reliable operation of a fluid feed pump and also makes a contribution to a space-saving construction and an improved service life.
  • the fact that transverse forces that act on the piston element during operation of the fluid delivery pump can be compensated or counteracted also reduces friction between the outer wall of the piston element and the inner wall of a piston guide, so that wear on these components is reduced.
  • the device can also include a piston guide, which is sleeve-shaped and in coordination with the piston element with the piston recess.
  • a wall thickness of a lower region of the piston guide, for example in the housing is significantly smaller than in an upper region of the piston guide, which would be assigned to the upper or the first piston section.
  • loads such as tension and friction
  • the elasticity provided by the piston recess on the piston element can therefore be increased by elasticity of the piston guide and contribute to a particularly flexible, reliable and low-wear device for a fluid feed pump.
  • the piston element is designed such that the ratio of the minimum cross-sectional area in the region of the piston recess and the first cross-sectional area in the first piston section is between 0.16 and 0.49 inclusive.
  • the piston recess can be in the form of one or more notches on the wall of the piston element or as a through going recess form a recess on the piston element.
  • the piston recess is formed on the wall of the piston element in a radially circumferential manner with respect to the longitudinal axis.
  • the piston element is preferably designed to be rotationally symmetrical or cylindrical in relation to the longitudinal axis.
  • the piston recess is limited rotationally symmetrically by the wall and forms, for example, an annular recess on the cylindrical piston element.
  • the wall of the piston element in the region of the piston recess is designed in the form of a segment of a circle with respect to a cross section along the longitudinal axis.
  • the bottom of the groove or the wall of the piston element that delimits the piston recess is then rounded off, for example in the form of a semicircle, in order to keep a notch effect on the piston element as low as possible.
  • other groove shapes are also possible.
  • the wall of the piston element in the region of the piston recess is, for example, trapezoidal or notch-shaped in relation to a cross section along the longitudinal axis.
  • the piston recess can be delimited in particular in a V-shape by the wall of the piston element.
  • the piston element as a whole such a limitation can be described as conical or conical.
  • the piston element has a second piston section as a further piston section and the piston recess is formed adjacent to the first and second piston sections, so that in relation to the Longitudinal axis of the first piston section has a first length and the first piston section, the region of the piston recess and the second piston section together have a second length or total length and the piston element is designed such that the ratio of the first length and the total length is between 0.7 and 0.9.
  • the piston recess can be provided at various points on the piston element, for example on the upper shaft, which is formed by the first piston section and cooperates with the piston guide in the fluid delivery pump, or also on the lower shaft, which is implemented, for example, by the further piston section is.
  • the piston recess is preferably provided in accordance with the specified ratio on a lower part of the upper piston section and, viewed from the upper end of the piston element, begins in the range from 70% to 90% of the total length of the upper shaft or of the first piston section.
  • the piston element has a second piston section as a further piston section and is designed such that the piston element has a second cross-sectional area with respect to the longitudinal axis in the second piston section, the size of which corresponds to the size of the first cross-sectional area in the first piston section is.
  • a piston element is then formed in one step with a shaft which is divided into sections by the piston recess into two pistons, an upper and a lower. Both piston sections then have, for example within the scope of manufacturing tolerances, essentially the same diameter.
  • the piston element has a third piston section as a further piston section. cut open and is formed such that the piston element has a third cross-sectional area with respect to the longitudinal axis in the third piston section, the size of which is smaller than the size of the first cross-sectional area in the first piston section and is larger than the size of the minimum
  • Such a piston element is then formed in two or more stages with two or more shafts, of which two adjacent shafts are separated by the piston recess or formulated differently, which are coupled to one another by means of the wall delimiting the piston recess.
  • the described embodiments of the device have advantageous effects with regard to the manufacture and operation of a fluid feed pump.
  • the load due to transverse forces that act on the piston element can be distributed over a larger area and thus reduced locally. This makes it possible to increase the service life and the robustness of the interacting components, and it contributes to less wear.
  • a length of the piston guide and thus further component lengths, such as that of the piston element, the piston guide sleeve and the housing can also be reduced. Cost savings can thus be realized.
  • a smaller installation space for the fluid feed pump which is advantageous for customer-oriented applications, can be realized in this way.
  • other materials for example materials with a lower hardness, can be used for the various components of the device, so that further cost savings are possible.
  • a fluid delivery pump comprises one of the previously described configurations of the device for Operating a fluid delivery pump for an internal combustion engine of a motor vehicle, which is arranged in or on the fluid delivery pump.
  • Figure 1 is a schematic representation of a force
  • FIG. 2 shows a schematic illustration of a device for operating a fluid delivery pump for the motor vehicle
  • Figures 3A-3C an embodiment of the device for
  • FIG. 4 shows a further exemplary embodiment of the device for operating a fluid delivery pump for the motor vehicle
  • FIGS. 5A-5B show a further exemplary embodiment of the device for operating a fluid feed pump for the motor vehicle
  • FIGS. 6A-6B show a further exemplary embodiment of the device for operating a fluid feed pump for the motor vehicle
  • Figures 7A-7B another embodiment of the device for operating a fluid feed pump for the motor vehicle.
  • Figure 1 shows a schematic representation of a motor vehicle 1 with an internal combustion engine 3 and a fluid feed pump 5 which is coupled to the internal combustion engine 3 to supply it with fuel during operation.
  • the fluid feed pump 5 has a device 10 which, as will be explained with reference to the following FIGS. 2 to 7B, enables inexpensive and space-saving production of the fluid feed pump 5 and also contributes to safe, reliable and long-lasting operation of the fluid feed pump 5.
  • the fluid feed pump 5 can in particular implement a high-pressure fuel pump in order to supply gasoline or diesel to the internal combustion engine.
  • the device 10 is shown in a schematic side view.
  • the device 10 for operating the fluid feed pump 5 for the motor vehicle 1 comprises a piston element 14 with a first piston section 11 and a second piston section 12, which extend in an elongated manner with respect to a longitudinal axis A of the piston element 14 and are coupled to one another (see FIG. 3A).
  • the device 10 further comprises a piston recess 15 which is formed on a wall 16 of the piston element 14 between the first piston section 11 and the second piston section 12.
  • the piston element 14 has in relation to the longitudinal axis A in the first piston section 11 has a first cross-sectional area Qi and a minimum cross-sectional area Q m in the region of the piston recess 15 and is designed such that the ratio of the minimum cross-sectional area Q m in the region of the piston recess 15 and the first cross-sectional area Qi in the first piston section
  • a hydraulic force acts on the piston element 14 due to the fluid pressure in the piston chamber, so that the piston element 14 is supported on an inside of the piston guide 17.
  • a force acts on the lower end of the piston element 14, which has a coupling interface 18 for connecting the roller tappet.
  • the piston recess 15 provides a certain elasticity and flexibility of the piston element 14, so that the lower piston section
  • FIGS. 3A to 3C show an exemplary embodiment of the device 10 and the piston element 14 and various cross sections.
  • the piston element 14 is rotationally symmetrical or cylindrical in shape with respect to the longitudinal axis A and has a first, a second and a third piston section 11, 12 and 13 along the longitudinal axis A.
  • the piston recess 15 is designed as an annular recess, which is set up in a radially circumferential manner with respect to the longitudinal axis A.
  • the piston sections 11, 12 and 13 are each formed essentially with a constant diameter.
  • the first and second piston sections 11 and 12 have essentially the same diameter.
  • the piston element 14 shown in FIG. 3A is designed in two stages or, in other words, has an upper and a lower shaft.
  • the upper shaft comprises the first and second piston sections 11, 12 and the piston recess 15 formed between these piston sections 11, 12.
  • the lower shaft is formed by the third piston section 13, to which the coupling interface 18 connects.
  • the first piston section 11 is therefore essentially located in the area within the piston guide 17 when the fluid feed pump 5 is in an assembled state and in operation, while the second and / or third piston section 12, 13 can also partially emerge therefrom, so that it is introduced in a targeted manner Piston recess 15 a predetermined changed leverage or torque on the first piston section 11 is adjustable, compared to a piston without such a recess.
  • the position of the piston recess 15 on the piston element 14 is preferably formed depending on an aspect ratio. Shown is a first length Li of the upper, first piston section 11 and a second length or a total length L 12 , which includes the length of the first piston section 11, the region of the piston recess 15 and the second piston section 12.
  • the piston recess 15 is preferably positioned such that the ratio of the first length L 2 and the total length L 12 is between 0.7 and 0.9. In this way, an elasticity and flexibility of the Kol benelements 14 can be established, which can have a particularly beneficial effect on operation within the piston guide 17 of the fluid feed pump 5.
  • FIGS. 3B and 3C illustrate cross sections perpendicular to the longitudinal axis A of the piston element 14 at the illustrated positions BB and AA.
  • the cross section BB thus shows the cross-sectional area Qi of the first piston section 11, which essentially also corresponds to a cross section of the second piston section 12.
  • the upper shaft with the piston sections 11, 12 has a predetermined diameter, which reduces to a predetermined minimum in the region of the piston recess 15.
  • the wall 16 of the piston element 14 is therefore specifically tapered, for example to form a cross-sectional ratio Q m / Qi, which is between 0.16 and 0.49. This range of values can also have an advantageous effect on the operation of the fluid pump 5 with regard to the elasticity and flexibility of the piston element 14.
  • FIG. 4 shows a further exemplary embodiment of the device 10 with the piston element 14 in a schematic side view.
  • the groove or the piston recess 15 is alternative positioned. It is formed on the lower shaft instead of on the upper shaft, wherein according to this embodiment the upper shaft comprises the first piston section 11 and the lower shaft the third piston section 13 with different diameters.
  • FIGS. 5A-7B illustrate, in schematic side views, exemplary embodiments with regard to the shape of the piston recess 15.
  • the piston recess 15 can be delimited in a segment of a circle by the associated wall 16 and represent a groove with a rounded bottom .
  • the piston recess 15 can be notched in the form of a notch by the associated wall 16 of the piston element 14 (see FIGS. 6A and 6B) and form a groove which tapers in a V-shape in the radial direction.
  • the piston recess 15 can also be trapezoidally delimited by the associated wall 16, so that the groove formed tapers conically in the radial direction to a certain section which has a smaller diameter than the first and second adjacent piston sections 11 and 12. While the minimum cross section Q m in the exemplary embodiments according to FIGS. 5A-5B and 6A-6B is essentially in the center of the piston recess 15 along a radial cross section perpendicular to the longitudinal axis A of the piston element 14, the exemplary embodiment according to FIGS. 7B has a certain section with a minimum diameter or with a minimum cross-sectional area Q m , which forms the bottom of the groove.
  • the specifically designed minimum cross-sectional area Q m in the region of the piston recess 15 is not necessarily the absolutely smallest cross-section of the piston element 14. This can also be formed, for example, at the lower end in the region of the coupling interface 18.
  • the trained minimum cross-sectional area Q m in the region of the piston recess 15 therefore realizes a predetermined minimum with respect to the adjacent piston sections 11 and 12 or 13.
  • the load due to transverse forces acting on the piston element 14 can be distributed over a larger area and thus locally reduced (see FIG. 2 ). This makes it possible to increase the service life and the robustness of the interacting components, and it contributes to less wear.
  • a length of the piston guide 17 and thus further component lengths, such as that of the piston element 14, a piston guide sleeve and a housing can be reduced. Cost savings can thus be realized.
  • a smaller space required for the fluid feed pump 5 can be realized in this way, which is advantageous for customer-oriented applications.
  • other materials for example materials with lower hardness, can be used for the various components of the device 10, so that further cost savings are possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif (10) pour faire fonctionner une pompe d'alimentation en fluide (5) pour un véhicule automobile (1), comprenant un élément de piston (14) ayant une première section de piston (11) et au moins une section de piston supplémentaire (12, 13), qui s'étendent longitudinalement par rapport à un axe longitudinal (A) de l'élément de piston (14) et sont couplées l'une à l'autre, et un évidement de piston (15) qui est formé sur une paroi (16) de l'élément de piston (14) entre la première section de piston (11) et la section de piston supplémentaire (12, 13). L'élément de piston (14) présente une première surface de section transversale (Q1) dans la première section du piston (11) par rapport à l'axe longitudinal (A) et une surface de section transversale minimale (Qm) dans la zone de la cavité du piston (15) et est conçu de telle sorte que le rapport entre la surface de section transversale minimale (Qm) dans la zone de la cavité du piston (15) et la première surface de section transversale (Q1 ) dans la première partie du piston (11) est inférieur à 0,75.
PCT/DE2019/200101 2018-09-25 2019-08-22 Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile Ceased WO2020064064A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018216371.5 2018-09-25
DE102018216371.5A DE102018216371A1 (de) 2018-09-25 2018-09-25 Vorrichtung zum Betreiben einer Fluidförderpumpe für ein Kraftfahrzeug und Fluidförderpumpe für ein Kraftfahrzeug

Publications (1)

Publication Number Publication Date
WO2020064064A1 true WO2020064064A1 (fr) 2020-04-02

Family

ID=67953509

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2019/200101 Ceased WO2020064064A1 (fr) 2018-09-25 2019-08-22 Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile

Country Status (2)

Country Link
DE (1) DE102018216371A1 (fr)
WO (1) WO2020064064A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1130250A1 (fr) * 2000-03-01 2001-09-05 Wärtsilä NSD Schweiz AG Pompe d'injection de carburant haute pression
DE10146745A1 (de) * 2001-09-22 2003-04-10 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
JP2011220194A (ja) * 2010-04-08 2011-11-04 Denso Corp 高圧ポンプ
DE102013224797A1 (de) * 2013-12-04 2015-06-11 Robert Bosch Gmbh Kraftstoffpumpe mit einem Kolben, an dessen einem Antrieb zugewandten Endabschnitt ein Federteiler angeordnet ist

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19527401A1 (de) * 1995-07-27 1997-01-30 Teves Gmbh Alfred Kolbenpumpe
DE19618013A1 (de) * 1996-05-04 1997-11-06 Teves Gmbh Alfred Kolben, insbesondere für eine Radialkolbenpumpe und Verfahren zu dessen Herstellung
DE102004061810A1 (de) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Kolbenpumpe mit wenigstens einem Stufenkolbenelement

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1130250A1 (fr) * 2000-03-01 2001-09-05 Wärtsilä NSD Schweiz AG Pompe d'injection de carburant haute pression
DE10146745A1 (de) * 2001-09-22 2003-04-10 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
JP2011220194A (ja) * 2010-04-08 2011-11-04 Denso Corp 高圧ポンプ
DE102013224797A1 (de) * 2013-12-04 2015-06-11 Robert Bosch Gmbh Kraftstoffpumpe mit einem Kolben, an dessen einem Antrieb zugewandten Endabschnitt ein Federteiler angeordnet ist

Also Published As

Publication number Publication date
DE102018216371A1 (de) 2020-03-26

Similar Documents

Publication Publication Date Title
DE102009003054A1 (de) Hochdruckpumpe
WO2016198193A1 (fr) Poussoir à galet pour pompe à piston, pompe à piston
DE102016218909A1 (de) Rollenstößel für eine Kolbenpumpe, Kolbenpumpe
DE102010063351A1 (de) Hochdruckpumpe
DE102006048722A1 (de) Kolbenpumpe, insbesondere Kraftstoffhochdruckpumpe, mit Rollenstößel
AT514966B1 (de) Ein Hochdruckmedium führendes Bauelement
EP2419635B1 (fr) Pompe à piston avec entraînement par came, en particulier pompe à carburant
DE102018124353A1 (de) Verstellvorrichtung für eine Axialkolbenmaschine
DE102017121425A1 (de) Pleuel für eine Brennkraftmaschine mit variabler Verdichtung
WO2020064064A1 (fr) Dispositif pour faire fonctionner une pompe d'alimentation en fluide pour un véhicule automobile et pompe d'alimentation en fluide pour un véhicule automobile
DE102009001633A1 (de) Hochdruckpumpe und Stößelbaugruppe
DE102008008438A1 (de) Hochdruckpumpe
EP2126356A1 (fr) Pompe à haute pression pour transporter du carburant avec un guidage amélioré du piston de pompe
WO2012080340A1 (fr) Pompe haute pression
DE102009047568A1 (de) Kraftstoffhochdruckpumpe
WO2017148841A1 (fr) Piston pour pompe à carburant haute pression à piston et pompe à carburant haute pression à piston
EP3339602B1 (fr) Bielle pour un moteur à combustion interne à compression variable
DE102015221296A1 (de) Rollenstößel für eine Kolbenpumpe, Kolbenpumpe
DE102008042182A1 (de) Kolbenpumpe mit kugelkalottenförmigen Lagerflächen für eine Laufrolle
DE102015103203A1 (de) Pleuelstange und Verbrennungsmotor
DE102006044294B3 (de) Radialkolbenpumpe
DE102009001440A1 (de) Hochdruckpumpe
EP1798415B1 (fr) Pompe à haute pression
EP2872778B1 (fr) Pompe à haute pression
WO2017055103A1 (fr) Pompe haute pression

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19768707

Country of ref document: EP

Kind code of ref document: A1

122 Ep: pct application non-entry in european phase

Ref document number: 19768707

Country of ref document: EP

Kind code of ref document: A1