EP3234343A1 - Pompe à carburant à piston pour moteur à combustion interne - Google Patents

Pompe à carburant à piston pour moteur à combustion interne

Info

Publication number
EP3234343A1
EP3234343A1 EP15805167.2A EP15805167A EP3234343A1 EP 3234343 A1 EP3234343 A1 EP 3234343A1 EP 15805167 A EP15805167 A EP 15805167A EP 3234343 A1 EP3234343 A1 EP 3234343A1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
seal
working space
end portion
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
EP15805167.2A
Other languages
German (de)
English (en)
Other versions
EP3234343B1 (fr
Inventor
Jochen Kaesser
Bernd Beiermeister
Soeren Stritzel
Wolfgang Ochs
Ralf Assmann
Heiko Jahn
Christian Preissner
Achim LAUB
Peter Ropertz
Stefan ZAENSCH
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 EP3234343A1 publication Critical patent/EP3234343A1/fr
Application granted granted Critical
Publication of EP3234343B1 publication Critical patent/EP3234343B1/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
    • F02M59/44—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0448—Sealing means, e.g. for shafts or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/143—Sealing provided on the piston
    • 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
    • F02M2200/8046—Fuel injection apparatus manufacture, repair or assembly the manufacture involving injection moulding, e.g. of plastic or metal
    • 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
    • F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit

Definitions

  • the invention relates to a piston fuel pump according to the preamble of claim 1.
  • the known from WO 2014095120 A1 piston fuel pump comprises a pump cylinder and a pump piston slidably received in the pump cylinder.
  • This piston fuel pump has a bearing and sealing arrangement for the pump piston, which comprises a guide region for the axial guidance of the pump piston in the pump cylinder and a sealing lip having a sealing lip.
  • a piston fuel pump for an internal combustion engine with a pump cylinder and a pump cylinder axially displaceable pump piston and with a limited by the pump piston working space, wherein on the pump piston, a seal is present, which seals the working space against a low pressure region, the Seal is applied directly to the pump piston by means of an injection molding process.
  • seal seals between a pump piston and
  • Direct application means, in particular, that the material of the seal is applied to the piston in the liquid state and then solidifies thereon, in particular solidifies as a result of cooling.
  • the direct application of the seal on the pump piston by means of an injection molding process has the advantage that a separate production of the seal and subsequent handling and connection with the pump piston is eliminated and thus simplifies the production. Furthermore, can be in this way a variety of geometrical configurations of the interface between seal and pump piston, in particular
  • seal also seals the working space end portion of the pump piston against the working space, in particular completely seals.
  • the entire pump piston is located on the side facing away from the working space side of the seal, ie in particular in a low-pressure region. In this way, a leakage between the working space and the low-pressure area, which may occur in the pump known from the prior art along a path extending between the pump piston and the seal, becomes complete and reliable
  • the working-chamber-side end section of the pump piston is understood to mean, in particular, a region which comprises the working space-side end face of the pump piston and also an end section of the pump piston pointing in the axial direction to the working space.
  • the workspace-side end section can be in particular the tapered part of the stepped piston and / or the region of the pump piston lying on the working space side of the stage.
  • the working space side end portion of the pump piston for example, based on the longitudinal extension of the pump piston, ie in the axial direction, be formed only in the working space side half of the pump piston or even only in the working space side in the axial direction outer quarter of the pump piston.
  • the sealing of the working chamber-side end portion of the pump piston against the working space through the seal can be realized in that the seal has a recess with particular cylindrical basic shape, in which the working space end portion of the pump piston is arranged and / or is filled by the working space side end portion of the pump piston , in particular completely filled out. In other words, the seal thus covers the particular
  • the gasket thus has, in yet other words, in particular a cup-shaped inner contour, in which the working chamber-side end portion of the pump piston is arranged and / or which is filled by the working space end portion of the pump piston, in particular completely filled.
  • cup-shaped here implies, in particular, the presence of a frontal bottom, which may be formed, for example, as a round surface, and a wall peripherally formed on the edge of the bottom, which may be in particular perpendicular to the bottom.
  • cylindrical basic shape includes, in particular, actually geometrically exact cylindrical shapes, but is fundamentally wide, in particular in the sense of "elongated” to understand and provides none
  • End portion of the pump piston and the seal are mutually positively.
  • the terms form fit and positive connection are used in the sense of VDI 2232;
  • the working space-side end portion of the pump piston and the seal are positively to each other when they are hooked into each other due to their shape.
  • the working space side end portion of the pump piston and the seal may be non-positively connected with each other, _
  • the seal may rest under tension on the working space side end portion of the pump piston.
  • the working space side end portion of the pump piston has a first surface structure and the seal a second
  • first surface structure and the second surface structure are complementary to each other and / or interlock.
  • the first surface structure and the second surface structure can fill each other, in particular completely fill.
  • a surface structure of the seal or of the pump piston is to be understood as meaning, in particular, geometric features which do not have the geometric basic shape of the seal or the geometry already discussed above
  • surface structures may only have features whose feature sizes are significantly smaller, for example not greater than 10%, as feature sizes of the seal and / or the working space end portion of the pump piston, for example the overall length, and / or the widest diameter of the seal and / or the pump piston and / or the working-side end portion of the
  • the surface structure of the seal or the pump piston can be any shape.
  • Surface structure is a knurled structure, in particular a
  • Cross knurl structure which can be applied to a pump piston in a simple manner.
  • knurled structure is used in particular
  • Structure sizes of geometrically regular surface structures in the axial and / or tangential direction are given in particular by their periodicity.
  • Structure sizes of geometrically regular surface structures in the radial direction are given in particular by their amplitude.
  • the surface structure of the seal and / or of the pump piston can also be geometrically irregular, for example realized by a, in particular comparatively high, roughness of the pump piston and / or the seal.
  • structure sizes in the axial and / or tangential and / or radial direction are likewise equally determinable on the basis of the variables known for characterizing surface roughness.
  • Pt and / or Rz and / or Ra can be understood as a structural depth.
  • the wavelength at which the maximum of a spectral decomposition of the surface roughness of the seal and / or of the pump piston obtained, in particular by Fourier transformation can be understood as a feature size in the axial and / or tangential direction.
  • surface structures with structure sizes in the radial direction in the range of 0.1 mm to 2 mm are advantageously possible.
  • the structure size in the radial direction ie the structure depth
  • the structure size in the radial direction is sufficiently large in the axial and / or tangential direction compared to the structure size, since this ensures the effect of a toothing.
  • the working-side end section of the pump piston has a first surface structure and the seal has a second surface structure and the first surface structure and / or the second surface structure have a structure depth measured in the radial direction and one measured in the tangential and / or axial direction
  • Has structure size and measured in the tangential and / or axial direction structure size is not more than 10 times the texture depth, preferably even not more than 5 times the texture depth.
  • the seal may in particular comprise a thermoplastic material or consist of a thermoplastic material.
  • the thermoplastic material "
  • thermoplastic polymer for example a fiber-reinforced thermoplastic polymer.
  • it may be carbon fiber reinforced polyetheretherketone (PEEK).
  • PEEK polyetheretherketone
  • PEEK 150CA30 Another preferred thermoplastic material is PA66CF20.
  • the seal has a thickness in the range of 0.5mm to 1, 8mm to ensure high strength, low mass and easy manufacturability alike.
  • the fuel piston pump is, in particular, a pump which has a pump housing in which a working chamber bounded by the pump piston is formed.
  • the compression of the fuel takes place in particular in this working space, in particular by an axial movement of the pump piston which reduces the working space.
  • the fuel in the working space is compressed to a high pressure level, for example to 100 bar to 600 bar.
  • the seal according to the invention is in particular formed between the working space and a low-pressure region of the pump.
  • Low pressure range is lower than the high pressure level generated in the workspace of the pump.
  • the pressure level in the low pressure range may be, for example, 3bar to 10bar and be generated by a separate backing pump.
  • the working space is in particular via an outlet valve with a
  • the electrically controllable inlet valve can be designed in particular as a quantity control valve.
  • Damping device to be provided for damping pulsations in the low pressure region of the pump.
  • the damping device for damping pulsations in the low-pressure region for example, an enclosed between two membranes
  • Gas volumes include details regarding the damping device may be formed as shown in DE10327408A1. _
  • a further valve arranged between the pump outlet and the working chamber, which is arranged antiparallel to the outlet valve, can be provided and in particular act as a pressure limiting valve for a high-pressure accumulator which can be connected to the pump.
  • the outlet valve and / or the inlet valve and / or the pressure relief valve are fixed to the pump housing and thus fixed in place to the pump cylinder.
  • a fixation of these components on the pump piston separates so far in particular. This results in the advantage that the mass of the pump piston is low and thus the dynamics or ease of the pump is improved.
  • the pump piston is designed as a solid body, so that it can withstand the high pressure during fuel injection, in particular in the gasoline direct injection, without deformation.
  • a flowability of the pump piston in the longitudinal direction separates so far.
  • Pressure relief valve to each other and in the pump body can
  • the pump cylinder may be formed in a sleeve fixed in the pump body. Alternatively, the pump cylinder may also be provided directly in the pump body.
  • the pump body, the pump piston, the pump cylinder, and / or all pump parts that come into contact with the fuel preferably consist only of steels and made of plastic, so that in the result a high
  • the objective is based on maximizing the life of the piston fuel pump. Furthermore, it has been recognized that wear occurring in the area of the seal is significantly caused by the friction occurring between the seal and the pump cylinder becomes.
  • the friction phenomena occurring can be divided into classes or phases according to DIN 50281.
  • friction partners In the case of fluid friction, on the other hand, direct contact between the friction partners no longer occurs.
  • the friction partners are separated by a liquid medium, for example by a continuous
  • Liquid film in this case for example by a continuous
  • mixed friction can occur, which has temporally and / or spatially next to each other shares of solid friction and shares of liquid friction.
  • a radially outer surface of the seal which faces an inner surface of the pump cylinder, is formed in an axial end portion of the seal so that it bears against the pump cylinder when the pump piston is stationary relative to the pump cylinder and that a relative movement between the pump cylinder and pump piston in the axial direction favors a lifting of the seal from the pump piston in a radially inward direction.
  • a radially outer surface of the seal which faces an inner surface of the pump cylinder, is inclined radially inwardly in an axial end region of the seal at an angle of 10 ° to 60 ° to the inner wall of the pump cylinder.
  • the fuel to be compressed by the pump piston in this case in particular exerts a radially inwardly acting force on the radially outer
  • FIG. 1 shows a schematic representation of a fuel system of a
  • FIG. 2 shows an enlarged sectional view of the detail of the piston fuel pump according to FIG. 1
  • a fuel system of an internal combustion engine bears the reference numeral 10 as a whole. It comprises a fuel tank 12, from which an electric prefeed pump 14 conveys the fuel into a low-pressure line 16. This leads to a high pressure pump in the form of a piston fuel pump 18. From this leads a high pressure line 20 to a Fuel rail 22. To this several injectors 24 are connected, which inject the fuel directly into each associated combustion chambers (not shown).
  • the piston fuel pump 18 includes only indicated in regions
  • Pump housing 26 in which a pump piston 28 is slidably guided or stored. This can be offset by a cam drive not shown in a reciprocating motion, which is indicated by a laterally drawn double arrow 30.
  • the pump piston 28 is of a
  • Coil spring 32 is acted upon in a bottom dead center in FIG. Of the
  • Pump piston 28 and the pump housing 26 define a working space 34.
  • This working space 34 is connected via an inlet valve 36 with the low pressure line 16. Furthermore, the working space 34 can be connected to the high-pressure line 20 via an outlet valve 38.
  • the intake valve 36 may be forcibly opened during a delivery stroke of the pump piston 28, so that the fuel is not delivered to the fuel rail 22 but back into the low-pressure passage 16. This can be promoted by the piston fuel pump 18 in the fuel rail 22
  • the pump piston 28 is guided in a pump cylinder 40, which is part of the pump housing 26 so far.
  • the pump piston 28 has at a
  • the pump piston 28 In the vicinity of this working-side end portion 42, the pump piston 28 also has an annular shoulder 44 in the manner of a radially projecting circumferential collar.
  • a seal 46 comes to rest on the pump piston 28 or on the shoulder 44 and encloses the working-space-side end section 42 of the pump piston 28 axially and radially. Thereby, the working space side end portion 42 of the pump piston 28, completely sealed against the working space 34, one in the working space
  • the medium is not in contact with the working space side end portion 42 of the pump piston 28 and a working in the working space effective hydraulic pressure thus acts on the working space side end portion 42 of the Pump piston 28 no longer or only indirectly via the seal 46 a.
  • the pump piston 28 At its end facing away from the working space 34, the pump piston 28 also has a lower end portion 52 in FIG. In the vicinity of this lower end portion 52, a guide sleeve 54 is fixedly mounted on the pump housing 26. Between the guide sleeve 54 and the pump housing 26, an O-ring seal 56 is provided in a groove 58.
  • the guide sleeve 54 has a cylinder portion 60 which extends coaxially with the pump piston 28 and through which the coil spring 32 is guided.
  • Coil spring 32 emerges along a piston longitudinal axis 62 at least partially into a spring receiving groove 64 of the guide sleeve 54, where it is axially supported against the guide sleeve 54.
  • the guide sleeve 54 also has inside a circular cylindrical
  • Receiving portion 66 which is formed substantially by the inner peripheral wall of the cylinder portion 60.
  • annular sealing member 68 is arranged stationary relative to the pump housing 26, wherein the sealing element 68 has an H-shaped cross-section.
  • a guide element 72 is also arranged so as to be stationary relative to the pump housing 26. This thus seen in the axial direction of the pump piston 28 of the seal 46 significantly spaced guide member 72 together the seal 46, the guide or two-point bearing of the pump piston 28 ready.
  • Figure 2 shows a sectional view of a section of the piston fuel pump 18, wherein the working space side end portion 42 of
  • the seal 46 has a recess 74 with a cylindrical shape, which is completely filled by the working space side end portion 42 of the pump piston 28, so that in cooperation with the between
  • Seal 46 and pump cylinder 40 existing sealing function of Workspace-side end portion 42 of the pump piston 28, completely sealed against the working space 34.
  • the seal 46 covers a
  • End portion 42 of the pump piston 28 is completely covered by the seal 46.
  • a sealing lip 50 is provided, which cooperates sealingly with the pump cylinder 40.
  • the seal 46 is made of the fiber reinforced in this example
  • thermoplastic polymer PEEK 150CA30 or PA66CF20 The gasket 46 is made by an injection molding process in which the liquefied
  • Piston longitudinal axis 62 on the working space side end portion 42 of the
  • Pump piston 28 is applied directly. It can be used for this purpose, for example, a hot runner tool in which the molten thermoplastic polymer in a between the working space side
  • Cavity is introduced at a relatively high temperature.
  • the gasket 46 has a thickness d of one millimeter, to ensure high strength, low mass and easy manufacturability alike.
  • the working space-side end portion 42 of the pump piston 28 and standing in contact with this inner contour of the recess 74 of the seal 46 has a substantially smooth surface.
  • Pump piston 28 formed groove structure is on the inner contour of the seal 46 is seen to be complementary, so as a negative image, formed, which in the present case results in the injection molding in a natural way.
  • the grooves have a depth t of only 0.1 mm and a periodicity in the axial direction x of 1 mm.
  • the grooves have a depth t of 2mm and a periodicity in the axial direction x of 9mm. These grooves can also be formed as shafts, see Figure 3c.
  • FIGS. 1-10 Examples of working-side end portions 42 of pump pistons 28 having relatively large grooves spaced from each other are shown in FIGS.
  • knurling structures or a cross knurl structures can also be provided on the working chamber-side end section 42 of the pump piston 28 and on the inner contour of the seal 46.
  • An example of such a working space side end portion 42 of a pump piston 28 is shown in Figure 3f.
  • irregular surface structures on the working space side end portion 42 of the pump piston 28 and on the inner contour of the seal 46 may be provided, which in particular represent a roughness of the pump piston 28 and the seal 46.
  • An axial end region 464 of the seal 46 is formed in the present case on the working side of the sealing lip 50. It is envisaged that a radially outer surface of the seal 46, which faces an inner surface of the pump cylinder 40, is inclined radially inwardly in an axial end portion 464 of the seal 46 at an angle ⁇ of 10 ° to 60 ° to the inner wall of the pump cylinder 40 , This has the effect or alternatively it is provided that a relative movement between the pump cylinder 40 and pump piston 28 in the axial direction, in particular in the direction of the working space 34, favors a lifting of the seal 46 from the pump cylinder 28 in a radially inward direction. In this case, a fluid film consisting of fuel is formed between the seal 46 and the pump cylinder 40, which considerably reduces the wear of the piston fuel pump 18 with slight leakage.
  • an outwardly facing, circumferential ridge 468 integrally formed which has approximately the shape of an isosceles triangle in cross-section in the longitudinal direction, of which the two opposite acute corners point in axial directions and the third blunt Corner of the pump cylinder 40 (static) is applied. It is provided that only this web (static) comes to rest on the pump cylinder 40, while the seal 46 or the sealing lip 50 is otherwise spaced by a gap 77 of the pump cylinder 40. A width s of the gap

Landscapes

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

Abstract

L'invention concerne une pompe à carburant à piston (18) pour un moteur à combustion interne, comprenant un cylindre de pompe (40) et un piston de pompe (28) qui peut coulisser dans le sens axial dans le cylindre de pompe (40), et comprenant un espace de travail (34) délimité par le piston de pompe (28). Une garniture d'étanchéité (46) est présente sur le piston de pompe (28), laquelle réalise l'étanchéité de l'espace de travail (34) par rapport à une zone à basse pression. L'invention est caractérisée en ce que la garniture d'étanchéité (46) est appliquée directement sur le piston de pompe (28) au moyen d'un procédé de moulage par injection.
EP15805167.2A 2014-12-17 2015-12-04 Pompe à carburant à piston pour moteur à combustion interne Active EP3234343B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014226304.2A DE102014226304A1 (de) 2014-12-17 2014-12-17 Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
PCT/EP2015/078694 WO2016096483A1 (fr) 2014-12-17 2015-12-04 Pompe à carburant à piston pour moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP3234343A1 true EP3234343A1 (fr) 2017-10-25
EP3234343B1 EP3234343B1 (fr) 2020-12-02

Family

ID=54783600

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15805167.2A Active EP3234343B1 (fr) 2014-12-17 2015-12-04 Pompe à carburant à piston pour moteur à combustion interne

Country Status (7)

Country Link
US (1) US10400727B2 (fr)
EP (1) EP3234343B1 (fr)
JP (1) JP6472522B2 (fr)
KR (1) KR20170093854A (fr)
CN (1) CN107110096A (fr)
DE (1) DE102014226304A1 (fr)
WO (1) WO2016096483A1 (fr)

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DE102014202794A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014202796A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014202795A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
KR20170032428A (ko) 2014-08-11 2017-03-22 후아웨이 테크놀러지 컴퍼니 리미티드 모바일 지불 방법 및 장치와 근거리 무선 통신 장치
DE102014226316A1 (de) * 2014-12-17 2016-06-23 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine

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CN107110096A (zh) 2017-08-29
EP3234343B1 (fr) 2020-12-02
JP6472522B2 (ja) 2019-02-20
DE102014226304A1 (de) 2016-06-23
US20170306912A1 (en) 2017-10-26
JP2017538891A (ja) 2017-12-28
WO2016096483A1 (fr) 2016-06-23
US10400727B2 (en) 2019-09-03
KR20170093854A (ko) 2017-08-16

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