WO2022189542A1 - Pompe à piston, en particulier pompe à carburant haute pression pour moteur à combustion interne - Google Patents

Pompe à piston, en particulier pompe à carburant haute pression pour moteur à combustion interne Download PDF

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Publication number
WO2022189542A1
WO2022189542A1 PCT/EP2022/056123 EP2022056123W WO2022189542A1 WO 2022189542 A1 WO2022189542 A1 WO 2022189542A1 EP 2022056123 W EP2022056123 W EP 2022056123W WO 2022189542 A1 WO2022189542 A1 WO 2022189542A1
Authority
WO
WIPO (PCT)
Prior art keywords
axial
pump
component
piston
seal
Prior art date
Application number
PCT/EP2022/056123
Other languages
German (de)
English (en)
Inventor
Kathrin Gerhard
Dominik NAAKE
Wolfgang Bueser
Matthias RIEDLE
Markus Goeke
Daniel HEINZINGER
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 WO2022189542A1 publication Critical patent/WO2022189542A1/fr

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
    • 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
    • F04B53/02—Packing the free space between cylinders and 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
    • 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
    • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections
    • F04B53/162—Adaptations of cylinders
    • F04B53/164—Stoffing boxes
    • 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
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders

Definitions

  • Piston pump in particular high-pressure fuel pump for a
  • the invention relates to a piston pump, in particular a high-pressure fuel pump for an internal combustion engine, according to the preamble of claim 1.
  • DE 102017212 498 A1 discloses a piston pump that can be used, for example, in internal combustion engines with direct gasoline injection.
  • Such piston pumps have a seal between the pump housing and the pump piston.
  • a sealing ring which is stationary relative to the pump housing and is made of a plastic material, is used as the seal.
  • the sealing ring is arranged between the pump housing and the pump piston in such a way that it is acted upon at least in some areas radially inwards against the pump piston by the pressure acting from the pumping chamber. It is thus “activated” as it were by the pressure acting from the pumping chamber.
  • the piston pump according to the invention has an increased service life and reliability without the efficiency, ie the delivery rate, of the piston pump being adversely affected. This is achieved in that the friction power between the annular seal and the pump piston is comparatively small in that the contact length between the annular seal and the pump piston is limited or reduced by the design-related change in rigidity.
  • the ring-shaped seal heats up only slightly due to the reduced friction, which means that the rigidity of the ring-shaped seal changes only slightly and the service life of the seal is increased. Due to the reduction in rigidity in that area in which the seal is acted upon by the pressure acting from the conveying chamber radially inwards, there is a faster concern, ie. faster "activation" of the seal is achieved.
  • a piston pump in particular a high-pressure fuel pump for an internal combustion engine.
  • the high-pressure fuel pump can be part of a fuel system, which compresses the fuel to a high pressure and injects it directly into the combustion chambers of the internal combustion engine.
  • the piston pump includes a pump housing, which can for example be an overall cylindrical part, as well as a pump piston which is accommodated in the pump housing in a receiving opening present there and which can be designed as a stepped piston, for example, and which is set in a reciprocating motion by a drive can.
  • a pumping chamber is delimited by the pump housing and the pump piston, into which fluid is sucked during a suction stroke and during a pumping stroke the fluid in the pumping chamber is compressed to a high pressure and discharged via an outlet valve.
  • An annular seal is arranged between the receiving opening of the pump housing and the pump piston in such a way that the pressure acting from the delivery chamber during a delivery stroke acts at least in some areas radially inwards against the pump piston.
  • the desired maximum sealing effect of the seal is therefore only brought about by the high pressure acting on the seal from radially outside to radially inside.
  • the annular seal has a higher radial rigidity in a first axial region, which faces the conveying chamber, than in a second axial region, which faces away from the conveying chamber. In this case, an axial extension of the first axial area, which has the higher radial rigidity, is greater than an axial extension of the second axial area, which consequently has a lower radial rigidity.
  • the longer, first axial area is thus pressed less strongly radially inward than the shorter, second axial area.
  • the contact length or friction length that is particularly effective for the hydraulic seal is thus essentially limited to the second axial region. Nevertheless, in the first axial area in the radial gap between the inside of the seal and the outside of the pump piston, a pressure drop and thus a certain sealing performance is already generated.
  • a gap dimension that is as small as possible can be set, for example, by honing the inside of the seal.
  • a radial stiffness difference of at least 5-8, preferably greater than 10 could be optimal for the usual plastics here.
  • a ring cross-section there is at least an approximately linear relationship, i.e. a ratio of the wall thicknesses of at least 5-8, preferably at least 10, between the two axial areas.
  • the seal could be thicker by this factor in the first axial area. If stronger or stiffer materials are used, such as steel, the factor given above can be correspondingly smaller, for example in the range of 3-5, but at least 2.
  • the axial extension of the first axial area is at least twice the axial extension of the second area.
  • An aspect ratio of at least 2, preferably in the range of about 2 to 3, provides optimal seal stability, sufficient pressure drop in the first axial region, and the desired short contact length in the second axial region.
  • the change in the radial rigidity from the first axial area to the second axial area is at least essentially stepped. In this way, a clear functional Separation created and the contact length in the second axial area is really limited to the desired low value. In principle, however, a continuous or semi-continuous change is also conceivable.
  • the first axial area has a first axial partial area and a second axial partial area, with the first axial partial area facing the pumping chamber and having a higher radial rigidity than the second axial partial area, which faces away from the pumping chamber.
  • this makes it possible to create the clear functional separation just mentioned between the first axial area and the second axial area, but at the same time this configuration helps to reduce or avoid stress peaks within the seal.
  • a material property in the first axial area differs from a material property in the second axial area in such a way that the radial rigidity in the first axial area is greater than in the second axial area.
  • the higher radial rigidity means that the material deforms less severely under the action of force, at least in the radial direction, i.e. it has an overall higher effective modulus of elasticity. Structural measures that would otherwise be necessary, such as the attachment of ribs, can thus be omitted or at least be less pronounced.
  • the seal comprises a fiber plastic material and that the fibers in the first axial area have a different orientation than in the second axial area, such that the radial rigidity in the first axial area is greater than in the second axial region.
  • the material can be a glass fiber-filled plastic.
  • PTFE may also be considered as a plastic.
  • the seal is a multi-component part with at least a first component and a second component, and that the first component is only in the first axial Area is arranged and has a relation to the second component increased radial stiffness. This is also a simple way of realizing a higher radial rigidity in the first axial area than in the second axial area.
  • the first component comprises a ring made of a material whose rigidity is greater than the rigidity of the material of the second component, in particular that the material of the first component comprises metal and that of the second component comprises plastic.
  • the ring has a first axial section facing the pumping chamber and a second axial section facing away from the pumping chamber, and that the first axial section of the ring has a higher radial rigidity than the second axial section.
  • this makes it possible to create the above-mentioned clear functional separation between the first axial area and the second axial area, but at the same time this configuration helps to reduce or avoid stress peaks within the seal.
  • the first component is accommodated in or on the second component, preferably cast into it or cast onto it. In this way, the first component is held securely in the second component, and multi-component injection molding is a proven and inexpensive manufacturing process.
  • FIG. 1 shows a partial longitudinal section through a piston pump with an annular seal and a pump piston
  • FIG. 2 shows a schematic, enlarged illustration of the annular seal and the pump piston from FIG. 1 in a first operating state
  • FIG. 3 shows an illustration similar to FIG. 2, in a second operating state
  • Figure 4 is a perspective view of a portion of a component of the annular seal of Figures 1-3;
  • Figure 5 is a perspective view of a portion of an alternative embodiment of the annular seal.
  • a piston pump in the form of a high-pressure fuel pump bears the reference numeral 10 overall in FIG. It usually delivers the fuel to a fuel rail to which a number of injectors are connected, which inject the fuel into the combustion chambers of the internal combustion engine.
  • the piston pump 10 includes an inlet valve, not shown, and an outlet valve, also not shown, as well as a pump housing 12.
  • a pump piston 14 is accommodated in this housing so that it can be moved back and forth.
  • the pump piston 14 is set in motion by a drive, not shown.
  • the drive can be, for example, a camshaft or an eccentric shaft of the internal combustion engine.
  • the pump piston 14 is designed here, for example, as a stepped piston with a section 16 with a smaller diameter and a section 18 with a larger diameter.
  • the pump piston 14 is received in the pump housing 14 in a receiving opening 22 present there, which is designed as a stepped bore 24 with sections 24', 24" and 24"' shown here, which each have different diameters.
  • An annular seal 26 is arranged between section 18 of pump piston 14 and an inner peripheral wall of bore 24 in the region of section 24". This seals directly between pump piston 14 and pump housing 12, and thus seals the The pumping chamber 20 ("high-pressure area") located in the annular seal 26 differs from the area (“low-pressure area”) arranged below the annular seal 26 in Figure 1. The precise design and function of the annular seal 26 will be discussed in greater detail below .
  • An annular guide element 28 separate from the annular seal 26 is arranged between the section 18 of the pump piston 14 and the inner peripheral wall of the bore 24 in the section 24 ′ thereof.
  • the guide element 28 is functionally located between the annular seal 26 and the pumping chamber 20. It is used to guide the pump piston 14.
  • a non-illustrated biasing element for example a spring, can be arranged between the guide element 28 and the annular seal 26, which the annular seal 26 in Figure 2 downwards against an annular holding element 30, which is arranged in section 24''" of the bore 24 or the receiving opening 22.
  • the annular seal 26 rests on the holding element 30 in such a way that a static sealing point is formed there, which the seal 26 seals against the holding element 30 .
  • the retainer 30 may be press fit into the pump housing 12 or it may be staked in the bore 24 or welded to the pump housing 12 .
  • the piston pump 10 has a further guide element 32 which is also ring-shaped and is arranged in a carrier 34 .
  • the guide element 32 also serves to guide the pump piston 14 relative to the pump housing 12.
  • the exact configuration of the ring-shaped seal 26 will now be explained with reference to FIG. 2: the ring-shaped seal 26 initially comprises a sleeve-shaped, cylindrical and comparatively long section 36 with a constant wall thickness D1 in FIG. 2 seen from top to bottom. This is followed by a comparatively short section 38 with a wall thickness D2 that is smaller than the wall thickness D1.
  • the seal 26 shown here as an example has an overall approximately L-shaped cross section.
  • the seal 26 is designed as a multi-component seal. It includes a first component 42 formed by a metal ring.
  • the metal ring 42 has a first axial partial area or section 44 which faces the delivery chamber 20 in the installed position and which is designed as a continuous material section in the circumferential direction.
  • tongue-shaped extensions 46 are formed, which point away from the delivery chamber 20 in the installation position shown in FIGS.
  • the tongue-shaped extensions 46 form a second axial partial area or section of the metal ring 42.
  • the metal ring 42 therefore has the overall shape similar to a crown.
  • the first axial section 44 has a higher radial rigidity than the second radial section 46, ie in the first axial section 44 a higher radial force is required for a specific radially inward deformation than for the same deformation in the second axial Section 46 is required.
  • the overall material property of the seal 26 in the axial area of the metal ring 42 differs from the overall material property of the seal 26 outside the axial area of the metal ring 42.
  • the seal 26 further includes a second component 48 which gives the seal 26 the overall L-shape.
  • the first component 42 ie the metal ring, is accommodated in the second component 48 in the area of the cylindrical section 36, in the present example cast, for example in a multi-component injection molding process.
  • the second material component 48 is a plastic in the present case.
  • FIG. 2 shows an initial situation as it exists when the piston pump 10 is not being operated. The same pressure prevails at all points on the outside of the seal 26, namely ambient pressure, and between an inner and, in this operating situation, straight lateral surface 50 of the annular seal 26 and an outer lateral surface 52 of the pump piston 14 there is a uniform gap 54 with a substantially constant thickness present.
  • This pressure P 20 also prevails in the upper region of the inner lateral surface 50 of the seal 26 in FIG. 3. In the gap 54 there is a flow through the gap 54 in FIG however, a pressure drop. In the area of the short section 38, the pressure acting on the inner lateral surface 50 of the seal 26 is thus significantly smaller than the pressure acting on the outer lateral surface 58 there.
  • first axial region 64 in which the first component 42 (metal ring) is arranged
  • second axial region 66 in which only the second component 48 (plastic) and If there is also a smaller wall thickness D2 due to the constriction 40, the seal 26 is pressed radially inwards in the area of the constriction 40, which is indicated by a hatched area 68 in FIG. Where the seal 26 is pressed radially inwards, it comes into contact with the pump piston 14 via an axially extending contact length area 70. In the contact length area 70, there is thus a particularly strong sealing effect, and as a result a correspondingly large pressure difference, as shown by the schematic diagram DR is shown in FIG.
  • the first axial area 64 which has a higher radial rigidity than the second axial area 66 due to the metal ring 42, has an axial extension that is greater by a factor of approximately 2.5 than the second axial area 66.
  • the fact that the metal ring 42 is present in the first axial area 64 results in a stepped change in the radial rigidity from the first axial area 64 to the second axial area 66 at the lower end of the metal ring 42 in Figure 3.
  • the second component 48 can be a plastic.
  • it can be a glass fiber-filled plastic, in which case, in addition or as an alternative to the above-mentioned metal ring 42 for adjusting the radial rigidity, the orientation of the fibers in a first axial area of the seal 26 can have a different orientation than in a second axial area.
  • FIG 5 an alternative embodiment of an annular seal 26 is shown.
  • the first component 42 is not accommodated in the second component, but instead accommodated on it, namely cast onto it on its inside.
  • the first component 42 is designed as a toothed metal ring.
  • the second axial portion or the Tongue-shaped extensions 46 unlike those of the embodiment of Figure 4, do not have a taper at their protruding ends, but instead an extension 72. This creates an "axial undercut 73" and a toothing with the second component 48, whereby the first component 42 (metal ring) is held particularly reliably on the second component 48.
  • the first component 42 is inserted into the injection molding tool as an insert when the ring-shaped seal 26 is injection molded and is guided and sealed inside and outside the injection molding tool 5, the upper edge of the first axial partial area 44 has a radially outward-pointing collar 74. This further increases the radial rigidity in this area.
  • the manufacturing tolerances of the inner diameter and the outer diameter of the first component 42 (metal ring) are smaller than the gap widths required for sealing in the injection molding tool, which are typically in the range of at least 20-30 ⁇ m for a PPS material.
  • the inner diameter of the first component 42 (metal ring) and the second component 48 are essentially the same.

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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)

Abstract

L'invention concerne une pompe à piston, en particulier une pompe à carburant haute pression pour un moteur à combustion interne, comprenant un carter de pompe, un piston de pompe (14), une chambre d'alimentation délimitée au moins par le carter de pompe et le piston de pompe (14), et un joint d'étanchéité annulaire (26) dont au moins une partie est agencée entre le carter de pompe et le piston de pompe (14) de sorte qu'au moins une partie dudit joint d'étanchéité est pressée contre le piston de pompe (14) par l'action de la pression à partir de la chambre d'alimentation, le joint d'étanchéité (26) présentant une rigidité radiale supérieure dans une première région axiale (64) qui fait face à la chambre d'alimentation à dans une seconde région axiale (66) orientée à l'opposé de la chambre d'alimentation. Selon l'invention, une extension axiale de la première région axiale (64) est supérieure à une extension axiale de la seconde région axiale (66).
PCT/EP2022/056123 2021-03-11 2022-03-10 Pompe à piston, en particulier pompe à carburant haute pression pour moteur à combustion interne WO2022189542A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021202371.1 2021-03-11
DE102021202371.1A DE102021202371A1 (de) 2021-03-11 2021-03-11 Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine

Publications (1)

Publication Number Publication Date
WO2022189542A1 true WO2022189542A1 (fr) 2022-09-15

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ID=80933804

Family Applications (1)

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PCT/EP2022/056123 WO2022189542A1 (fr) 2021-03-11 2022-03-10 Pompe à piston, en particulier pompe à carburant haute pression pour moteur à combustion interne

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Country Link
DE (1) DE102021202371A1 (fr)
WO (1) WO2022189542A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006029391A1 (de) * 2006-06-27 2008-01-03 Robert Bosch Gmbh Fahrzeugbremsanlagen-Kolbenpumpe mit einer Kolbendichtung
DE102017203083A1 (de) * 2017-02-24 2018-08-30 Aktiebolaget Skf Schaftdichtung
DE102017212498A1 (de) 2017-07-20 2019-01-24 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
US20190170137A1 (en) * 2017-12-01 2019-06-06 Gardner Denver Petroleum Pumps Llc Header ring

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006029391A1 (de) * 2006-06-27 2008-01-03 Robert Bosch Gmbh Fahrzeugbremsanlagen-Kolbenpumpe mit einer Kolbendichtung
DE102017203083A1 (de) * 2017-02-24 2018-08-30 Aktiebolaget Skf Schaftdichtung
DE102017212498A1 (de) 2017-07-20 2019-01-24 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
US20190170137A1 (en) * 2017-12-01 2019-06-06 Gardner Denver Petroleum Pumps Llc Header ring

Also Published As

Publication number Publication date
DE102021202371A1 (de) 2022-09-15

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