EP3234343B1 - Pompe à carburant à piston pour moteur à combustion interne - Google Patents
Pompe à carburant à piston pour moteur à combustion interne Download PDFInfo
- Publication number
- EP3234343B1 EP3234343B1 EP15805167.2A EP15805167A EP3234343B1 EP 3234343 B1 EP3234343 B1 EP 3234343B1 EP 15805167 A EP15805167 A EP 15805167A EP 3234343 B1 EP3234343 B1 EP 3234343B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- piston
- seal
- working chamber
- end section
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000000446 fuel Substances 0.000 title claims description 49
- 238000002485 combustion reaction Methods 0.000 title claims description 5
- 239000012815 thermoplastic material Substances 0.000 claims description 6
- 239000004696 Poly ether ether ketone Substances 0.000 claims description 5
- 238000001746 injection moulding Methods 0.000 claims description 5
- 229920002530 polyetherether ketone Polymers 0.000 claims description 5
- 230000000295 complement effect Effects 0.000 claims description 3
- 238000000465 moulding Methods 0.000 claims description 2
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 claims 1
- 229910052799 carbon Inorganic materials 0.000 claims 1
- 230000001737 promoting effect Effects 0.000 claims 1
- 238000007789 sealing Methods 0.000 description 15
- 238000004519 manufacturing process Methods 0.000 description 6
- 229920001169 thermoplastic Polymers 0.000 description 6
- 238000013016 damping Methods 0.000 description 5
- 238000002347 injection Methods 0.000 description 5
- 239000007924 injection Substances 0.000 description 5
- 239000007788 liquid Substances 0.000 description 5
- 238000011161 development Methods 0.000 description 4
- 230000018109 developmental process Effects 0.000 description 4
- 239000007787 solid Substances 0.000 description 4
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 229920000049 Carbon (fiber) Polymers 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 239000004917 carbon fiber Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000012528 membrane Substances 0.000 description 1
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000035699 permeability Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 230000003595 spectral effect Effects 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 230000003746 surface roughness Effects 0.000 description 1
Images
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.
- piston fuel pump comprises a pump cylinder and a pump piston slidably received in the pump cylinder.
- This piston fuel pump has a mounting and sealing arrangement for the pump piston, which comprises a guide area for axially guiding the pump piston in the pump cylinder and a sealing area having a sealing lip.
- DE102013226062 A1 discloses another piston fuel pump.
- a piston fuel pump according to claim 1 is provided.
- the seal seals a gap between the pump piston and the pump cylinder.
- direct application is understood in particular to mean that the material of the seal is applied to the piston in a liquid state and then solidifies on the piston, in particular solidifies as a result of cooling.
- the direct application of the seal to the pump piston by means of an injection molding process has the advantage, on the one hand, that a separate production of the seal and subsequent handling and connection to the pump piston are not required, and production is thus simplified. Furthermore, diverse geometric configurations of the interface between the seal and the pump piston, in particular form-fitting connections, can easily be implemented in this way.
- seal also seals off the end section of the pump piston on the working space side from the working space, in particular completely sealing it off.
- the entire pump piston is located on the side of the seal facing away from the working chamber, that is to say in particular in a low-pressure region. In this way, leakage between the working space and the low-pressure area, which can occur in the pump known from the prior art along a path running between the pump piston and seal, is completely and reliably excluded.
- the end section of the pump piston on the working chamber side is understood in particular to be a region which comprises the end face of the pump piston on the working chamber side and also an end portion of the pump piston pointing in the axial direction towards the working chamber.
- the end section on the working space side can in particular be the tapered part of the stepped piston and / or the area of the pump piston on the working space side of the step.
- the end section of the pump piston on the working chamber side can, for example, be formed only in the working chamber-side half of the pump piston in relation to the longitudinal extension of the pump piston, i.e. in the axial direction, or even only in the working chamber-side outer quarter of the pump piston in the axial direction.
- the sealing of the working chamber-side end section of the pump piston against the working chamber by the seal can be realized in that the seal has a recess with an especially cylindrical basic shape, in which the working chamber-side end section of the pump piston is arranged and / or which is filled by the working chamber-side end section of the pump piston , in particular is filled in completely.
- the seal covers, in particular, the end section of the pump piston on the working space side, both radially and on the end face of the pump piston facing the working space.
- the seal has, in particular, a cup-shaped inner contour in which the end section of the pump piston on the working chamber side is arranged and / or which is filled, in particular completely filled, by the end portion of the pump piston on the working chamber side.
- cup-shaped here implies in particular the presence of an end-face base, which can be designed as a round surface, for example, and a wall formed around the edge of the base, which can in particular extend perpendicular to the base.
- cylindrical basic shape in particular also actually includes geometrically exact cylindrical shapes, but is basically to be understood broadly, in particular in the sense of “elongated” and does not represent any restriction with regard to surface structures that can be formed on the pump piston and on the seal and which will be discussed in more detail below.
- the end section of the pump piston on the working space side and the seal can be connected to one another in a force-locking manner, In particular, the seal can rest under tension on the end section of the pump piston on the working space side.
- the end section of the pump piston on the working space side has a first surface structure and the seal has a second surface structure and the first surface structure and the second surface structure are complementary to one another and / or engage in one another.
- the first surface structure and the second surface structure can fill one another, in particular fill them completely.
- a surface structure of the seal or the pump piston is understood to mean in particular geometric features that do not relate to the basic geometric shape of the seal or the pump piston already discussed above.
- surface structures can only have features whose structure sizes are significantly smaller, for example not greater than 10%, than structure sizes of the seal and / or the end section of the pump piston on the working space side, for example the total length and / or the widest diameter of the seal and / or the pump piston and / or the end section of the pump piston on the working chamber side.
- the surface structure of the seal is either a grooved structure and / or a wave structure, in particular with grooves and / or waves that run radially around the end section of the pump piston on the working space side, or a knurled structure, in particular a cross-knurled structure, which is simple and easy on a pump piston Way can be applied.
- the term knurled structure is understood in particular with reference to DIN 82 from 1973. 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.
- surface structures with structure sizes in the radial direction in the range from 0.1 mm to 2 mm are advantageously possible.
- Deep structures for example with structure sizes in the radial direction of 0.5 mm or more, have the advantage of being particularly effective Toothing between the end section of the pump piston on the working chamber side and the seal.
- flat structures for example with structure sizes in the radial direction of 0.5 mm or less, have the advantage that they are particularly easy to manufacture.
- the structure size in the radial direction ie the structure depth
- the structure size in the axial and / or tangential direction is sufficiently large in comparison to the structure size in the axial and / or tangential direction, since this ensures the effect of a toothing.
- the seal can in particular have a thermoplastic material or consist of a thermoplastic material.
- the thermoplastic material can in particular be a thermoplastic polymer, for example a fiber-reinforced thermoplastic polymer. It can be, for example, polyetheretherketone (PEEK) reinforced with carbon fiber. One such is, for example, PEEK 150CA30. Another preferred thermoplastic material is PA66CF20.
- the seal has a thickness in the range from 0.5mm to 1.8mm to ensure high strength, low mass and easy manufacture.
- the fuel piston pump is, in particular, a pump that has a pump housing in which a working space delimited 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 that reduces the working space.
- the fuel in the working chamber is compressed to a high pressure level, for example to 100 bar to 600 bar.
- the seal according to the invention is formed in particular between the working space and a low-pressure area of the pump.
- the pressure in the low pressure area is lower than the high pressure level that is generated in the working area of the pump.
- the pressure level in the low pressure range can be, for example, 3 to 10 bar and can be generated by a separate backing pump.
- the working space is connected in particular to a pump outlet via an outlet valve and in particular connected to a pump inlet via an electrically controllable inlet valve.
- the electrically controllable inlet valve can in particular be designed as a quantity control valve.
- a damping device for damping pulsations in the low-pressure region of the pump can also be provided between the pump inlet and the working chamber.
- the damping device for damping pulsations in the low-pressure range can, for example, comprise a gas volume enclosed between two membranes; details regarding the damping device can be as in FIG DE10327408A1 be formed shown.
- Another 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 that can be connected to the pump.
- the outlet valve and / or the inlet valve and / or the pressure limiting valve are preferably fixed in a fixed position to the pump housing and, to this extent, also fixed in a fixed position to the pump cylinder. A fixation of these components on the pump piston is excluded in particular. There is the advantage that the mass of the pump piston is low and thus the dynamics or ease of movement of the pump is improved.
- the pump piston is preferably designed as a solid body so that it can withstand the high pressures that act during fuel injection, in particular during gasoline direct injection, without deformation.
- a permeability of the pump piston in the longitudinal direction is ruled out in this respect.
- FIG DE102004013307A1 Further details of the arrangement of the working chamber, outlet valve and pressure relief valve to one another and in the pump body can be, for example, as in FIG DE102004013307A1 be formed shown.
- the pump cylinder can be formed in a bushing fixed in the pump body. Alternatively, the pump cylinder can 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 are preferably only made of steel and plastic, so that the result is high resistance to fuels containing ethanol and / or other aggressive fuels .
- the friction phenomena that occur can be divided into classes or phases according to DIN 50281, depending on the type of contact conditions between the friction partners, here the seal and the pump cylinder.
- the friction partners are separated from one another by a liquid medium, for example by a continuous liquid film, in the present case for example by a continuous fuel film.
- the frictional forces that occur are usually considerably lower than with solid body friction. The wear that occurs on the friction partners is correspondingly reduced.
- mixed friction can also occur which, temporally and / or spatially, has proportions of solid body friction and proportions of liquid friction.
- a radially outer surface of the seal which lies opposite an inner surface of the pump cylinder, is designed in an axial end region of the seal in such a way that it rests 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 the 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 is opposite an inner surface of the pump cylinder, is inclined radially inward 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 exerts, in particular, a radially inward force on the radially outer surface of the seal, so that it can in particular lift slightly from the pump cylinder and a fuel film can in particular form between the seal and the pump cylinder.
- a fuel system of an internal combustion engine contributes to Figure 1 generally the reference numeral 10. It comprises a fuel tank 12, from which an electrical 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 a high pressure line 20 leads to a fuel rail 22. A plurality of injectors 24 are connected to this, which inject the fuel directly into combustion chambers (not shown) assigned to them.
- the piston fuel pump 18 comprises a pump housing 26, only partially indicated, in which a pump piston 28 is displaceably guided or mounted. This can be set in a back and forth movement by a cam drive (not shown), which is indicated by a double arrow 30 drawn on the side.
- the pump piston 28 is converted into an in Figure 1 applied to lower dead center.
- the pump piston 28 and the pump housing 26 delimit a working space 34.
- This working space 34 can be connected to the low-pressure line 16 via an inlet valve 36.
- the working chamber 34 can be connected to the high-pressure line 20 via an outlet valve 38.
- Both the inlet valve 36 and the outlet valve 38 are designed as check valves.
- An embodiment of the inlet valve 36 as a quantity control valve is not shown, but possible.
- the inlet valve 36 can be forcibly opened during a delivery stroke of the pump piston 28, so that the fuel is not delivered into the fuel rail 22, but back into the low-pressure line 16. In this way, the amount of fuel delivered by the piston fuel pump 18 into the fuel rail 22 can be adjusted.
- the pump piston 28 is guided in a pump cylinder 40, which in this respect is part of the pump housing 26.
- the pump piston 28 has an end facing the working chamber 34 in Figure 1 end portion 42 arranged above. In the vicinity of this end section 42 on the working space side, the pump piston 28 furthermore has an annular shoulder 44 in the manner of a radially protruding circumferential collar.
- a seal 46 comes to rest on the pump piston 28 or on the shoulder 44 and surrounds the end section 42 of the pump piston 28 on the working space side axially and radially.
- the end section 42 of the pump piston 28 on the work space side is completely sealed off from the work space 34, i.e. a medium located in the work space does not come into contact with the end section 42 of the pump piston 28 on the work space side and a hydraulic pressure effective in the work space thus acts on the end section 42 of the work space Pump piston 28 no longer or only indirectly via seal 46.
- the pump piston 28 also has an in Figure 1 lower end portion 52.
- a guide sleeve 54 is fixedly arranged on the pump housing 26.
- An O-ring seal 56 is provided in a groove 58 between the guide sleeve 54 and the pump housing 26.
- the guide sleeve 54 has a cylinder section 60 which extends coaxially to the pump piston 28 and through which the helical spring 32 is guided.
- the helical spring 32 dips along a piston longitudinal axis 62, at least in sections, 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 in the interior a circular cylindrical receiving section 66 which extends essentially through the inner peripheral wall of the cylinder portion 60 is formed.
- an annular sealing element 68 is arranged in a stationary manner relative to the pump housing 26, the sealing element 68 having an H-shaped cross section.
- a guide element 72 is also arranged in a stationary manner relative to the pump housing 26. This guide element 72, which is clearly spaced apart from the seal 46 in the axial direction of the pump piston 28, together provides the seal 46 with the guidance or two-point mounting of the pump piston 28.
- Figure 2 shows a sectional view of a detail of the piston fuel pump 18, the working chamber-side end section 42 of the pump piston 28 and the seal 46 being shown enlarged.
- the seal 46 has a recess 74 with a cylindrical shape, which is completely filled by the end section 42 of the pump piston 28 on the work space side, so that in cooperation with the sealing function existing between the seal 46 and the pump cylinder 40, the end section 42 of the pump piston 28 on the work space side completely against the work space 34 is sealed.
- the seal 46 covers an end face 421 of the end section 42 of the pump piston 28 on the work space side and, in direct molding, a jacket surface 422 of the end section 42 of the pump piston 28 on the work space side, so that the end section 42 of the pump piston 28 on the work space side is completely covered by the seal 46.
- a sealing lip 50 is provided radially on the outside of the seal 46 and cooperates in a sealing manner with the pump cylinder 40.
- the seal 46 consists of the fiber-reinforced thermoplastic polymer PEEK 150CA30 or PA66CF20.
- the seal 46 is produced by an injection molding process, in which the liquefied thermoplastic polymer in the axial injection direction, along the Piston longitudinal axis 62, is applied directly to the end section 42 of the pump piston 28 on the working chamber side.
- a hot runner tool can be used for this, in which the melted thermoplastic polymer is introduced at a relatively high temperature into a cavity formed between the end section 42 of the pump piston 28 on the working space side and an injection mold.
- the pump piston 28 with the seal 46 attached to it can be removed from the injection mold.
- the seal 46 has a thickness d of one millimeter in order to ensure high strength, low mass and simple manufacture at the same time.
- the end section 42 of the pump piston 28 on the working space side and the inner contour of the seal 46 have circumferential grooves.
- the grooves have a depth t of 0.5 mm and a periodicity in the axial direction x of 1 mm. It can be a large number of grooves, each of which runs around in a closed manner.
- the circumferential grooves can, however, also represent a single or multiple thread in their entirety.
- the groove structure on the surface of the end section 42 of the pump piston 28 on the working space side is clearly complementary on the inner contour of the seal 46, that is, as a negative image, which in the present case results naturally in injection molding.
- 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 2 mm and a periodicity in the axial direction x of 9 mm. These grooves can also be designed as waves, see Figure 3c .
- FIG Figures 3d and 3e Examples of end sections 42 of the pump piston 28 on the working space side with relatively large grooves which are further spaced apart are shown in FIG Figures 3d and 3e shown.
- knurled structures or a cross-knurled structure can also be provided on the end section 42 of the pump piston 28 on the working space side and on the inner contour of the seal 46.
- An example of such an end section 42 of a pump piston 28 on the working space side is shown in FIG Figure 3f shown.
- irregular surface structures can of course also be provided on the end section 42 of the pump piston 28 on the working space side and on the inner contour of the seal 46, which in particular represent a roughness of the pump piston 28 and the seal 46.
- the Pt value of a measurement of the surface of the pump piston is 0.2 mm and the wavelength at which the maximum of a spectral decomposition of the surface roughness (Ra spectrum) occurs is 1 mm.
- An axial end region 464 of the seal 46 is formed in the present case on the working space side on the sealing lip 50. It is provided that a radially outer surface of the seal 46, which is opposite an inner surface of the pump cylinder 40, is inclined radially inward in an axial end region 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 pump cylinder 40 and pump piston 28 in an axial direction Direction, in particular in the direction of the working chamber 34, favors a lifting of the seal 46 from the pump cylinder 28 in a radially inwardly pointing direction. In this case, a liquid film consisting of fuel is formed between the seal 46 and the pump cylinder 40, which, in the event of a slight leak, considerably reduces the wear on the piston fuel pump 18.
- an outwardly facing, circumferential web 468 is integrally formed on or on the sealing lip 50, which has the shape of an isosceles triangle in cross section in the longitudinal direction, of which the two opposite pointed corners point in axial directions and the third is obtuse Corner on the pump cylinder 40 (static) rests. It is provided that only this web (statically) comes into contact with the pump cylinder 40, while the seal 46 or the sealing lip 50 is otherwise spaced apart from the pump cylinder 40 by a gap 77. A width s of the gap 77 is 20 ⁇ m, for example. In the event of a relative movement, as described above, a lifting of the web 468 from the pump cylinder 40 is also provided.
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- 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)
Claims (13)
- Pompe à carburant à piston (18) pour un moteur à combustion interne comprenant un cylindre de pompe (40) et un piston de pompe (28) déplaçable axialement dans le cylindre de pompe (40) et un espace de travail (34) limité par le piston de pompe (28), dans lequel un joint d'étanchéité (46) est prévu au niveau du piston de pompe (28), lequel joint d'étanchéité réalise l'étanchéité de l'espace de travail (34) vis-à-vis d'une région basse pression, caractérisée en ce que le joint d'étanchéité (46) est appliqué directement sur le piston de pompe (28) grâce à un procédé de moulage par injection et en ce que la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) comprend une première structure de surface (68) et le joint d'étanchéité (46) comprend une deuxième structure de surface (86) et la première structure de surface (68) et la deuxième structure de surface (86) sont complémentaires l'une à l'autre et/ou viennent en prise l'une dans l'autre ; et en ce que la première structure de surface (68) est une structure moletée ou en ce que la première structure de surface (68) est une structure rainurée ou ondulée s'étendant radialement autour de la partie d'extrémité (42) du piston de pompe (28).
- Pompe à carburant à piston (18) selon la revendication 1, caractérisée en ce que le joint d'étanchéité (46) réalise complètement l'étanchéité de la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) vis-à-vis de l'espace de travail (34) .
- Pompe à carburant à piston (18) selon la revendication 1 ou 2, caractérisée en ce que la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) présente une forme de base cylindrique et le joint d'étanchéité (46) comprend un évidement (72) présentant une structure de base cylindrique dans laquelle la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) est disposée.
- Pompe à carburant à piston (18) selon la revendication 1 ou 2, caractérisée en ce que la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) présente une forme de base cylindrique et le joint d'étanchéité (46) comprend un évidement (72) présentant une structure de base cylindrique, lequel évidement est rempli par la partie d'extrémité (42), côté espace de travail, du piston de pompe (28).
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) et le joint d'étanchéité (46) sont de formes complémentaires l'un par rapport à l'autre.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que la première structure de surface (68) et la deuxième structure de surface (86) se remplissent réciproquement.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que la première structure de surface (68) et la deuxième structure de surface (86) présentent une profondeur de structure (t), mesurée dans la direction radiale, dans la plage de 0,1 mm à 2 mm.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que la première structure de surface (68) et la deuxième structure de surface (86) présentent une périodicité dans la plage de 0,4 mm à 8 mm.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que la première structure de surface (68) et la deuxième structure de surface (86) présentent une profondeur de structure (t) mesurée dans la direction radiale et une périodicité et la périodicité est un multiple (v) de la profondeur de structure (t) mesurée dans la direction radiale, le multiple allant du double au décuple.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (46) est retenu à force sur la partie d'extrémité (42), côté espace de travail, du piston de pompe (28).
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (46) comprend une matière thermoplastique en particulier renforcée par des fibres, par exemple une polyétheréthercétone renforcée par des fibres de carbone.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce que le joint d'étanchéité (46) présente une structure de base annulaire, et est surmoulé par moulage par injection directement sur la partie d'extrémité (42), côté espace de travail, du piston de pompe (28) dans la direction de moulage par injection axiale.
- Pompe à carburant à piston (18) selon l'une des revendications précédentes, caractérisée en ce qu'une face, située radialement à l'extérieur, du joint d'étanchéité (46), laquelle est en regard d'une face intérieure du cylindre de pompe (40), est formée dans une région d'extrémité axiale (464) du joint d'étanchéité (46) de telle sorte qu'elle s'appuie contre le cylindre de pompe (40) lorsque le piston de pompe (28) est au repos par rapport au cylindre de pompe (40), et en ce qu'un mouvement relatif entre le cylindre de pompe (40) et le piston de pompe (28) dans la direction axiale favorise un soulèvement du joint d'étanchéité (46) du cylindre de pompe (40) dans une direction orientée radialement vers l'intérieur, en particulier le favorise de telle sorte qu'une face, située radialement à l'extérieur, du joint d'étanchéité (46), laquelle est en regard d'une face intérieure du cylindre de pompe (40), est inclinée radialement vers l'intérieur suivant un angle de 10° à 60° par rapport à la paroi intérieure du cylindre de pompe (40) dans une région d'extrémité axiale (464) du joint d'étanchéité (46).
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 EP3234343A1 (fr) | 2017-10-25 |
EP3234343B1 true 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) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014202796A1 (de) * | 2014-02-17 | 2015-08-20 | Robert Bosch Gmbh | Kolben-Kraftstoffpumpe für eine Brennkraftmaschine |
DE102017212498A1 (de) | 2017-07-20 | 2019-01-24 | Robert Bosch Gmbh | Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
DE102020214632A1 (de) * | 2020-11-20 | 2022-05-25 | Robert Bosch Gesellschaft mit beschränkter Haftung | Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine |
Family Cites Families (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1802281A (en) | 1929-02-13 | 1931-04-21 | Wilson Snyder Mfg Company | Slush pump |
US4245654A (en) * | 1977-03-22 | 1981-01-20 | Concord Laboratories, Inc. | Blood sampling syringe |
JPS63172061A (ja) | 1986-12-29 | 1988-07-15 | Daido Metal Kogyo Kk | 密封装置 |
JPH0642141Y2 (ja) | 1988-10-14 | 1994-11-02 | エヌオーケー株式会社 | 密封装置 |
DE19618013A1 (de) * | 1996-05-04 | 1997-11-06 | Teves Gmbh Alfred | Kolben, insbesondere für eine Radialkolbenpumpe und Verfahren zu dessen Herstellung |
ATE236368T1 (de) | 1996-07-30 | 2003-04-15 | Burckhardt Compression Ag | Verfahren zur herstellung eines dichtelementes sowie dichtelement hergestellt nach dem verfahren |
JP3886604B2 (ja) | 1997-07-07 | 2007-02-28 | 株式会社技術開発総合研究所 | ラジアルプランジャポンプ |
JP3607579B2 (ja) | 2000-07-06 | 2005-01-05 | 日精樹脂工業株式会社 | 射出成形用金型装置及び射出成形方法 |
WO2002095234A1 (fr) * | 2001-04-27 | 2002-11-28 | Hydrocision, Inc. | Cartouches de pompage haute pression destinees a des applications de pompage ou de perfusion medicales ou chirurgicales |
DE10362411B3 (de) | 2002-10-19 | 2017-09-07 | Robert Bosch Gmbh | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
DE102004013307B4 (de) | 2004-03-17 | 2012-12-06 | Robert Bosch Gmbh | Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil |
US20080098886A1 (en) | 2006-10-27 | 2008-05-01 | Hydro-Components Research And Development Corporation | Piston assembly and method of manufacturing piston assembly |
DE102009028131A1 (de) * | 2009-07-30 | 2011-02-03 | Trelleborg Sealing Solutions Germany Gmbh | Dichtung und Dichtungsanordnung |
CN102770217B (zh) * | 2009-12-11 | 2016-01-13 | 苏舍米克斯帕克有限公司 | 料筒活塞 |
JP5764337B2 (ja) * | 2011-02-01 | 2015-08-19 | アルバック機工株式会社 | シール部材の製造方法及び成形装置 |
US20140207075A1 (en) * | 2011-05-20 | 2014-07-24 | Coki Engineering Inc. | Skived film for covering surface of plug for medical purposes, plug for medical purposes using said film, pre-filled syringe using said plug and method for producing said film |
DE102012204302A1 (de) | 2012-03-19 | 2013-09-19 | Robert Bosch Gmbh | Umspritztes Bauelement mit einem Dichtlabyrinth |
DE102012213002A1 (de) * | 2012-07-24 | 2014-01-30 | Schwäbische Hüttenwerke Automotive GmbH | Nockenwellen-Phasensteller mit Dichtungshülse |
US10767644B2 (en) * | 2012-12-20 | 2020-09-08 | Robert Bosch Gmbh | Piston fuel pump for an internal combustion engine |
DE102014202794A1 (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 |
DE102014202796A1 (de) * | 2014-02-17 | 2015-08-20 | Robert Bosch Gmbh | Kolben-Kraftstoffpumpe für eine Brennkraftmaschine |
CN106170926A (zh) | 2014-08-11 | 2016-11-30 | 华为技术有限公司 | 移动支付的方法、装置及近场通信设备 |
DE102014226316A1 (de) * | 2014-12-17 | 2016-06-23 | Robert Bosch Gmbh | Kolben-Kraftstoffpumpe für eine Brennkraftmaschine |
-
2014
- 2014-12-17 DE DE102014226304.2A patent/DE102014226304A1/de not_active Withdrawn
-
2015
- 2015-12-04 EP EP15805167.2A patent/EP3234343B1/fr active Active
- 2015-12-04 US US15/527,827 patent/US10400727B2/en active Active
- 2015-12-04 WO PCT/EP2015/078694 patent/WO2016096483A1/fr active Application Filing
- 2015-12-04 CN CN201580069523.4A patent/CN107110096A/zh active Pending
- 2015-12-04 KR KR1020177016638A patent/KR20170093854A/ko unknown
- 2015-12-04 JP JP2017532630A patent/JP6472522B2/ja active Active
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
JP2017538891A (ja) | 2017-12-28 |
WO2016096483A1 (fr) | 2016-06-23 |
DE102014226304A1 (de) | 2016-06-23 |
US10400727B2 (en) | 2019-09-03 |
CN107110096A (zh) | 2017-08-29 |
JP6472522B2 (ja) | 2019-02-20 |
KR20170093854A (ko) | 2017-08-16 |
EP3234343A1 (fr) | 2017-10-25 |
US20170306912A1 (en) | 2017-10-26 |
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