EP4048885A1 - Pompe à carburant à haute pression - Google Patents

Pompe à carburant à haute pression

Info

Publication number
EP4048885A1
EP4048885A1 EP20780178.8A EP20780178A EP4048885A1 EP 4048885 A1 EP4048885 A1 EP 4048885A1 EP 20780178 A EP20780178 A EP 20780178A EP 4048885 A1 EP4048885 A1 EP 4048885A1
Authority
EP
European Patent Office
Prior art keywords
valve
holding element
fuel pump
pressure fuel
pressure
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.)
Withdrawn
Application number
EP20780178.8A
Other languages
German (de)
English (en)
Inventor
Rainer Kornhaas
Lars Gonnermann
Stephan Wehr
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP4048885A1 publication Critical patent/EP4048885A1/fr
Withdrawn legal-status Critical Current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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
    • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
    • 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
    • F02M59/46—Valves
    • F02M59/462—Delivery valves
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves

Definitions

  • the invention relates to a high-pressure fuel pump for a fuel injection system of an internal combustion engine according to the preamble of claim 1.
  • High pressure fuel pumps are known from the prior art.
  • Such a high-pressure fuel pump has a pressure limiting valve which, in an open state, connects an outlet-side high-pressure area to a delivery chamber of the high-pressure fuel pump.
  • the pressure limiting valve opens when a pressure difference between the outlet-side high-pressure area and the delivery chamber of the high-pressure fuel pump exceeds a limit value. The pressure limiting valve thus prevents the pressure in the outlet-side high-pressure area from being inadmissibly high.
  • the high-pressure fuel pump according to the invention for a fuel injection system of an internal combustion engine compresses the fuel to one high pressure and conveys it to injection devices that inject the fuel directly into the respective assigned combustion chambers of the internal combustion engine.
  • the high-pressure fuel pump has a pump housing, a recess arranged in the pump housing in which a pressure limiting valve is arranged, the pressure limiting valve comprising a valve body, a valve element, a holding element and at least one valve spring, the holding element between the valve element and the valve spring is arranged and is designed such that it is guided in a straight line in the recess.
  • the pressure-limiting valve limits the pressure in an outlet-side high-pressure area of the high-pressure fuel pump to a maximum permissible value. If the pressure prevailing there exceeds the opening pressure of the pressure relief valve, the valve element is moved against the force of the valve spring so that fuel can flow back from the high pressure area into a delivery chamber and / or a low pressure area in the high pressure fuel pump.
  • Undesired wear and cavitation erosion can occur on the surfaces between the valve element and valve body as well as on the surfaces between the valve element and the holding element. According to the current state of knowledge, the wear is caused, among other things, by an axial and radial movement of the holding element.
  • the cavitation erosion is caused when the pressure relief valve is opened by the movement of the holding element and by the vapor generated in the suction phases of the high-pressure fuel pump.
  • the movement of the holding element is in turn caused by pressure pulsations in the delivery chamber of the high-pressure fuel pump and an axial and radial oscillation of the valve spring.
  • the holding element Due to the straight guidance of the holding element according to the invention, it is reliably held straight, especially when opening and closing, and this reduces both wear and tear and cavitation erosion and thus extends the service life of the pressure relief valve and, with it, that of the high-pressure fuel pump.
  • Straight guidance means that the holding element is guided in the mostly cylindrical and linearly extending recess in such a way that it moves in a straight line, for example not tilting relative to a longitudinal axis of the recess or shifting in a direction lateral to the longitudinal axis can.
  • the straight guidance of the holding element within the recess the radial movement of the holding element is reduced, since the holding element is arranged with an accurate fit in the recess and is guided (with a sliding fit).
  • the holding element has a minimally smaller outer diameter than the inner diameter of the recess, so that a movement of the holding element within the recess in the direction of the diameter is prevented or at least minimized.
  • the axial movement of the holding element that is to say the movement in the longitudinal direction of the recess, is also damped. This happens due to the friction between the recess and the holding element guided therein. It is obvious that the outside of the holding element, which is in contact with the inside of the recess, must have a minimum extension in the axial direction in order to be able to achieve the desired stabilization function.
  • the holding element has a cylindrical section which extends in the axial direction and which has the maximum diameter of the holding element. In this way, straight guidance can be ensured without the holding element tilting within the recess.
  • the holding element have a receptacle for the valve element, the receptacle having a contact surface and at least one wall.
  • the recording is thus designed in the manner of a depression.
  • Such a contact surface is preferably oriented perpendicular to the axial direction of the holding element, that is to say also perpendicular to the longitudinal extent of the recess of the pressure limiting valve.
  • a receptacle with such a contact surface represents a structurally simple way of receiving the valve element in the axial direction of the holding element, holding it in the radial direction and exerting a uniform surface pressure.
  • the contact surface and the wall are arranged with respect to one another in such a way that they form a cylindrical or an at least partially spherical receiving space for the valve element.
  • the wall is intended to restrict the movement of the valve element in the radial direction of the holding element or to fix the valve element in the radial direction of the holding element.
  • the valve element can nevertheless have a certain amount of play within the fixing by the wall.
  • the contact surface and the wall are arranged at least partially perpendicular to one another.
  • the valve element can be accommodated both in the radial and in the axial direction of the holding element in a structurally very simple manner.
  • Such a recording can be realized, for example, by means of a blind hole-like bore in the holding element.
  • the holding element have at least one fluid connection between a side facing the valve body and a side facing away from the valve body.
  • the fluid connection is in particular arranged in such a way that as much fuel (fluid / liquid) as possible can flow through the holding element. If a certain amount of fuel has to flow through the retaining element, the flow speed of the fuel is reduced by a fluid connection that is as large as possible, i.e. a fluid connection with the largest possible flow cross-section, or as many fluid connections as possible that result in the largest possible flow cross-section overall . Movements of the holding element and cavitation effects, which occur with rapidly flowing liquids, are reduced by a low flow speed, or they even do not occur at all. This improves the “connection” of the valve seats, ie the surfaces between valve element and valve body or between valve element and retaining element, to the delivery chamber of the high-pressure fuel pump, which leads to a further reduction in cavitation erosion.
  • the fluid connection comprises at least one hole penetrating the holding element. This makes it possible, for example, to use the holding element as a rotating part to manufacture on a lathe. Such a manufacturing method can be advantageous over other manufacturing methods, e.g. B. cheaper.
  • the fluid connection comprises an overall essentially annular passage with connecting ribs.
  • the connecting ribs which preferably extend in the radial direction, connect a radially inner material section with a radially outer material section.
  • the connecting ribs are preferably evenly distributed in the circumferential direction.
  • connection of the valve seats to the delivery chamber of the high-pressure fuel pump is in turn improved.
  • the flow cross-section of the fluid connection is comparatively large, so that the flow velocity of the fuel (of the fluid) is comparatively small and thus the cavitation effects are also low.
  • the valve element be designed spherically.
  • Such a valve element is very easy to manufacture and easy to handle, whereby the manufacturing costs can be kept low.
  • the spherical valve element touches the contact surface at a single point and the wall touches the wall at most with its circumference. This minimizes the contact areas between the holding element and the valve element.
  • the spherical valve element preferably does not touch the wall in the closed state of the pressure relief valve. When the pressure relief valve is closed, the spherical valve element is radially centered via the valve seat in the valve body.
  • the holding element have at least one extension which is at least partially designed as a spring guide for the valve spring, for example in the form of a cylindrical protruding extension extending inside the spring.
  • the extension can preferably extend in the axial direction over a length of approximately two spring turns of the valve spring.
  • the pressure limiting valve have a valve spring guide element.
  • the valve spring guide element is arranged at least partially in the area of the end of the valve spring facing away from the holding element. It is designed in such a way that the valve spring is guided by the valve spring guide element in the region of the end of the valve spring facing away from the holding element.
  • the extension preferably extends so far in the direction of the holding element that the latter can just reliably execute a sufficient opening movement.
  • the holding element is a component produced by powder injection molding.
  • the holding element can also be manufactured as a turned part.
  • powder injection molding relatively complex shapes can also be produced, in particular curved channels, etc. Production as a turned part, on the other hand, is comparatively inexpensive.
  • FIG. 1 shows a section through a high-pressure fuel pump according to the invention with a pressure limiting valve
  • FIG. 2 shows a longitudinal section through the pressure relief valve according to FIG. 1;
  • FIG. 3 shows a perspective section through a region of the pressure limiting valve according to FIG. 1;
  • FIG. 4 shows a section through a holding element of the pressure limiting valve according to FIG. 1;
  • FIG. 5 shows a side view, a view from above and a view from below of the holding element according to FIG. 1;
  • FIG. 6 shows a perspective view, a view from above and a view from below of the holding element together with a valve element according to FIG. 1;
  • FIG. 7 shows a longitudinal section similar to FIG. 2 through a further exemplary embodiment of the pressure limiting valve
  • FIG. 8 shows two perspective views of the holding element of the pressure relief valve according to FIG. 7;
  • FIG. 9 shows a plan view of the holding element together with the valve element according to FIG. 7;
  • FIG. 10 shows a longitudinal section similar to FIG. 2 through a further exemplary embodiment of the pressure limiting valve
  • FIG. 11 shows two perspective views of the holding element of the pressure limiting valve according to FIG. 10;
  • FIG. 12 shows a plan view of the holding element together with the valve element according to FIG. 10;
  • FIG. 13 shows a longitudinal section similar to FIG. 2 through a further exemplary embodiment of the pressure limiting valve;
  • FIG. 14 shows two perspective views of the holding element of the pressure limiting valve according to FIG. 13.
  • FIG. 15 shows a plan view of the holding element together with the valve element according to FIG. 13.
  • a high-pressure fuel pump for an internal combustion engine bears the overall reference numeral 10.
  • the high-pressure fuel pump 10 has an essentially cylindrical pump housing 12 in or on which the essential components of the high-pressure fuel pump 10 are arranged.
  • the high-pressure fuel pump 10 has an inlet / quantity control valve 14, a delivery piston 18 which is arranged in a delivery chamber 16 and can be set in a reciprocating motion by a drive shaft (not shown), an outlet valve 20 and a pressure limiting valve 22.
  • first channel 24 which extends coaxially to the delivery chamber 16 and to the delivery piston 18 and which leads from the delivery chamber 16 to a second channel in the form of an essentially cylindrical recess 26 which is at an angle of 90 ° to the first channel 24 is arranged and in which the pressure relief valve 22 is received.
  • a longitudinal axis of the pump housing 12 bears the reference symbol 28, and a longitudinal axis of the recess 26 bears the reference symbol 29.
  • the delivery piston 18, which moves back and forth parallel to the longitudinal axis 28, is fed during a suction stroke with fuel - z. B. gasoline or diesel fuel - sucked into the pumping chamber 16 via the inlet / quantity control valve 14.
  • the fuel in delivery space 16 is compressed and ejected via outlet valve 20, for example, into a high pressure area 30, for example to a fuel collecting line (“rail”), where the fuel is stored under high pressure.
  • the high pressure area 30 is over an outlet port 32 is connected to the high-pressure fuel pump 10.
  • the amount of fuel that is expelled during a delivery stroke is set by the electromagnetically actuated inlet / quantity control valve 14.
  • the pressure-limiting valve 22 opens, as a result of which fuel can flow from the high-pressure area into the delivery chamber 16.
  • the pressure relief valve 22 connects, as said, in an open state the high pressure area 30 with the delivery chamber 16 of the high pressure fuel pump 10.
  • the pressure relief valve 22 opens when a pressure difference between the outlet side high pressure area 30 and the delivery chamber 16 of the high pressure fuel pump 10 a Exceeds limit.
  • the pressure limiting valve 22 therefore prevents the pressure in the outlet-side high-pressure region 30 from being inadmissibly high.
  • FIG. 2 shows a section through the pressure limiting valve 22 according to FIG. 1.
  • the pressure limiting valve 22 initially has a sleeve-like valve body 34 which is pressed into the recess 26 and in which a stepped channel 36 running in the longitudinal direction 29 of the valve body 34 is present.
  • a valve seat 38 is formed on the valve body 34 and cooperates with a valve element 40 in the form of a valve ball.
  • a holding element 42 is arranged on the side of the valve element 40 facing away from the valve seat 38.
  • the holding element 42 is essentially cylindrical and in this exemplary embodiment has three fluid connections 44, a contact surface 46 and three walls 48 (see also FIGS. 5 and 6).
  • the walls 48 are formed by the respective radially inward inner side of three extensions which are arranged on the side of the holding element 42 facing the valve body 34 and on the left in FIG.
  • the holding element 42 is guided straight in the recess 26 due to the cylindrical shape of the holding element 42 in a sliding fit. That is, the holding element 42 moves in a straight line within the recess 26 and parallel to the longitudinal axis 29. By guiding the holding element 42 in the recess 26, the radial movement of the holding element can be prevented or at least reduced.
  • the precisely fitting, cylindrical shape of the holding element 42 prevents the holding element 42 from tilting during a reciprocating movement in the axial direction Direction, that is parallel to the longitudinal axis 29, avoided or at least reduced when the pressure limiting valve 22 is opened or closed.
  • the holding element 42 is held straight even in the closed state of the pressure relief valve 22.
  • a valve spring 50 designed as a compression spring is arranged or braced between the holding element 42 and the end of the recess 26 on the right in FIG.
  • the valve element 40 is therefore acted upon by means of the valve spring 50 via the holding element 42 towards the valve seat 38.
  • the valve element 40 is centered relative to the holding element 42 and to the longitudinal axis 29 by the contact surface 46 and the valve seat 38.
  • FIG. 3 shows a section through a perspective detail of the pressure limiting valve 22 according to FIG. 1.
  • the valve body 34, the valve element 40, the holding element 42 and a detail of the valve spring 50 can be seen.
  • FIG. 4 shows a section through the holding element 42 according to FIG. 1. Here it can be seen particularly clearly that an angle of 90 ° is spanned between the contact surface 46 and the walls 48.
  • FIG. 5 shows a side view, a view from above and a view from below of the holding element 42 according to FIG. 1.
  • the course of the three fluid connections 44 is clearly illustrated here:
  • the fluid connections 44 as a whole form an essentially annular passage with three connection ribs (without reference numerals ), which are designed as extensions in the direction of the valve body 34.
  • the extensions of the connecting ribs each form a wall 48 with their side facing the longitudinal axis 29, that is to say radially inwardly (inner side).
  • the walls 48 together with the axial contact surface 46 form a receptacle 45 for the valve element 40.
  • FIG. 6 shows a perspective view, a view from above and a view from below of the holding element 42 together with the valve element 40 according to FIG. 1.
  • the three figures illustrate the seat of the valve element 40 in the holding element 42 and in the receptacle 45 the spherical valve element 40 and the holding element 42 are essentially point-shaped with respect to the contact surface 46 and with respect to the walls 48 linear.
  • the linear or punctiform contact between the valve element 40 and the holding element 42 creates a comparatively direct “connection” of the valve seats to the delivery chamber 16.
  • Such a “connection” leads to a comparatively low pressure difference across the holding element 42 and to lower forces acting on the holding element 42, which ultimately leads to less wear on the holding element 42.
  • the point contact between the valve element 40 and the contact surface 46 of the holding element 42 prevents or at least reduces the transmission of transverse forces / moments from the holding element 42 to the valve element 40. This leads to an at least substantially transverse force / torque-free valve seat and thus to a uniform surface pressure. This results in less wear.
  • the area of the holding element 42 subject to pressure is kept small.
  • the hydraulic forces that act on the holding element 42 are thus kept low, and the axial movement of the holding element 42 is thus reduced. This leads to less wear.
  • the measures described above ensure that cavitation erosion is also reduced on the valve seats.
  • the more direct "connection" of the valve seats to the pumping chamber 16 reduces cavitation erosion due to the formation of steam in the suction phases in the high-pressure fuel pump 10.
  • the reduction in the axial movement of the holding element 42 leads to fewer opening processes of the pressure relief valve 22, which in turn leads to less cavitation erosion.
  • the reduction of the radial movement of the holding element 42 and the suppression of transverse forces / moments on the valve element 40 lead to a comparatively uniform surface pressure and thus to fewer opening processes of the pressure limiting valve 22 and thus also to less cavitation erosion.
  • FIG. 7 shows a section through a further exemplary embodiment of the pressure limiting valve 22.
  • This exemplary embodiment differs from the previous one in that the holding element 42 has three extensions 52 on its side facing the valve spring 50. These serve at least partially as a guide for the valve spring 50.
  • the pressure limiting valve 22 also has a valve spring guide element 54.
  • the valve spring 50 is guided at least partially in the axial direction, that is to say parallel to the longitudinal direction 29, by the valve spring guide element 54.
  • the valve spring 50 is thus at least partially guided axially in a straight line by the extensions 52 and the valve spring guide element 54. As a result, undesired vibrations of the valve spring 50 in the radial direction can be avoided or at least reduced.
  • FIG. 8 The two perspective views of the holding element 42 in FIG. 8 and the top view of the holding element 42 together with the valve element 40 in FIG. 9 illustrate the holding element 42 according to the exemplary embodiment from FIG. 7.
  • FIG. 10 shows a section through a further exemplary embodiment of the pressure relief valve 22.
  • This exemplary embodiment differs from the previous one in that the fluid connections 44 are designed as bores which penetrate the holding element 42 and run axially, i.e. parallel to the longitudinal direction 29. It is therefore possible to produce this holding element 42 as a turned part by means of a lathe.
  • the holding element 42 has three extensions 52, which are configured somewhat longer in comparison to the previous exemplary embodiment of the pressure limiting valve 22. This results in better guidance of the valve spring 50 in the area of the end of the valve spring 50 on the left in FIG. 10.
  • FIG. 11 The two perspective views of the holding element 42 in FIG. 11 and the top view of the holding element 42 together with the valve element 40 in FIG. 12 illustrate the holding element 42 according to the exemplary embodiment from FIG. 10.
  • FIG. 13 shows a section through a further exemplary embodiment of the pressure limiting valve 22.
  • This exemplary embodiment differs from the preceding one in that the holding element 42 is designed as a rotating part with a deeply set valve element 40.
  • the walls 48 is not implemented by extensions, as in the exemplary embodiments described above, but by a central, spherical recess which is essentially complementary to the spherical valve element 40.
  • the pressure limiting valve 22 does not have a valve spring guide element 54.
  • a holding element 42 described as a rotating part can also be used with a different method, e.g. B. Metal Injection Molding (MIM) can be produced.
  • MIM Metal Injection Molding

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne une pompe à carburant à haute pression (10) destinée à un système d'injection de carburant d'un moteur à combustion interne, comprenant un carter de pompe (12) et un évidement (26) disposé dans le carter de pompe (12) dans lequel est agencée une soupape de limitation de pression (22), la soupape de surpression (22) comprenant un corps de soupape (34), un élément de soupape (40), un élément de retenue (42) et au moins un ressort de soupape (50), l'élément de retenue (42) étant disposé entre l'élément de soupape (40) et le ressort de soupape (50). Selon l'invention, l'élément de retenue (42) est conçu de manière à être guidé en ligne droite dans l'évidement (26).
EP20780178.8A 2019-10-23 2020-09-24 Pompe à carburant à haute pression Withdrawn EP4048885A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019216314.9A DE102019216314A1 (de) 2019-10-23 2019-10-23 Kraftstoff-Hochdruckpumpe
PCT/EP2020/076701 WO2021078464A1 (fr) 2019-10-23 2020-09-24 Pompe à carburant à haute pression

Publications (1)

Publication Number Publication Date
EP4048885A1 true EP4048885A1 (fr) 2022-08-31

Family

ID=72644253

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20780178.8A Withdrawn EP4048885A1 (fr) 2019-10-23 2020-09-24 Pompe à carburant à haute pression

Country Status (6)

Country Link
EP (1) EP4048885A1 (fr)
JP (1) JP2022553723A (fr)
KR (1) KR20220083725A (fr)
CN (1) CN114630955A (fr)
DE (1) DE102019216314A1 (fr)
WO (1) WO2021078464A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023013984A1 (fr) 2021-08-05 2023-02-09 주식회사 엘지에너지솔루션 Appareil de séchage permettant de fabriquer une électrode et procédé de fabrication d'électrode utilisant ce dernier

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004013307B4 (de) * 2004-03-17 2012-12-06 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
DE102016218215A1 (de) * 2016-09-22 2018-03-22 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
JP2019002374A (ja) * 2017-06-19 2019-01-10 ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング 高圧燃料ポンプ

Also Published As

Publication number Publication date
CN114630955A (zh) 2022-06-14
KR20220083725A (ko) 2022-06-20
JP2022553723A (ja) 2022-12-26
DE102019216314A1 (de) 2021-04-29
WO2021078464A1 (fr) 2021-04-29

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