WO2023104620A1 - Pompe à piston, en particulier pompe à carburant haute pression pour un moteur à combustion interne - Google Patents

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

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Publication number
WO2023104620A1
WO2023104620A1 PCT/EP2022/084006 EP2022084006W WO2023104620A1 WO 2023104620 A1 WO2023104620 A1 WO 2023104620A1 EP 2022084006 W EP2022084006 W EP 2022084006W WO 2023104620 A1 WO2023104620 A1 WO 2023104620A1
Authority
WO
WIPO (PCT)
Prior art keywords
seal
pump
piston
piston pump
section
Prior art date
Application number
PCT/EP2022/084006
Other languages
German (de)
English (en)
Inventor
Jurij Giesler
Frank Nitsche
Siamend Flo
Andreas Jesse
Guido Bredenfeld
Stephan Wehr
Ekrem CAKIR
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
Priority to CN202280081383.2A priority Critical patent/CN118369508A/zh
Publication of WO2023104620A1 publication Critical patent/WO2023104620A1/fr

Links

Classifications

    • 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
    • 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
    • F04B1/0439—Supporting or guiding means for the 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
    • 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
    • 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
    • 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
    • F02M2200/90—Selection of particular materials
    • F02M2200/9015—Elastomeric or plastic materials

Definitions

  • Piston pump in particular high-pressure fuel pump for an internal combustion engine
  • 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 by the pressure acting from the pumping chamber, at least in some areas, radially inwards against the pump piston and axially against a mating surface assigned to the pump housing. It is thus quasi “activated” by the pressure acting from the pumping chamber. In addition, it is acted upon axially by a spring device against the mating surface associated with the pump housing.
  • a piston pump in particular a high-pressure fuel pump for an internal combustion engine.
  • a high-pressure fuel pump is used both in diesel and in gasoline internal combustion engines. It usually compresses the fuel to a very high pressure and feeds it into a fuel collection line ("rail"), from where the fuel is injected directly into associated combustion chambers of the internal combustion engine by means of injectors.
  • the piston pump according to the invention comprises a pump piston which is a receiving opening of a pump housing is received. The pump housing, together with the pump piston and possibly other components, delimits a pumping chamber in which the fuel can be compressed.
  • a seal which at least temporarily interacts with the pump piston is arranged in the form of a ring around the pump piston. This is typically ring-shaped or sleeve-shaped. It seals a radial gap between the pump piston and the pump housing, "radial” being understood here and below as a direction that is at least approximately orthogonal to the longitudinal axis of the above-mentioned receiving opening in the pump housing or orthogonal to the longitudinal axis of the pump piston.
  • the seal is therefore arranged in regions between the pump housing and the pump piston and essentially coaxially with the pump piston.
  • a radial inner surface of the seal lies at least in regions on a radial outer surface of the pump piston.
  • at least one area of an end face of the seal rests axially against a mating surface that is assigned to the pump housing and is arranged on the side of the seal that faces away from the pumping chamber.
  • This counter surface can be created, for example, by an annular end face of a retaining ring, which is accommodated in a recess in the pump housing, for example pressed into it and/or welded to the pump housing.
  • the abutment of the radial inner surface of the seal on the pump piston and the axial front surface of the seal on the counter surface is caused in the piston pump according to the invention as well as in corresponding seals from the prior art during normal operation of the piston pump, in particular by a comparatively high hydraulic pressure acting from the pumping chamber acts on a radial outer surface of the seal and on a surface of the seal acting away from the delivery chamber in the axial direction.
  • the desired maximum sealing effect of the seal thus only occurs after the piston pump has started operating. The seal is thus "activated" by the start of operation of the piston pump.
  • the piston pump according to the invention also includes an annular section which is arranged in a ring shape around the pump piston and seen in the axial direction between the seal and the pumping chamber. According to the invention it is provided that the ring-shaped section is directly adjacent to the seal.
  • a spring which in conventional piston pumps acts on the seal against the counter surface, is therefore no longer present in the piston pump according to the invention.
  • the seal is thus “free” insofar as its radial movement is not restricted by a spring contacting it.
  • the seal is thus held in the axial direction between the mating surface and the annular section with little axial play. This enables the advantage mentioned at the outset that the seal centers itself hydraulically.
  • the seal as mentioned above, can be activated, in the area of the mutually adjacent ends of the ring-shaped section and seal, for example between the ring-shaped Section and the seal, at least one substantially radially extending flow passage present. Even if the seal is (still) in contact with the ring-shaped section at the start of operation of the piston pump, the pressure build-up radially outside of the seal is thus ensured.
  • the flow cross section of the flow passage should be dimensioned in such a way that there is almost no throttling. In any event, the pressure drop across the flow passage should be significantly less than the pressure drop across the initial gap between the seal and mating surface.
  • At least one flow passage is present in or on the seal, for example in or on an edge facing the annular section. Since the seal is usually made of plastic, this is easy to produce.
  • At least one flow passage is present in or on the ring-shaped section, for example in or on an edge facing the seal.
  • the ring-shaped section is a guide section for the pump piston.
  • the ring-shaped section can preferably be provided as a guide element which is separate from the pump housing and which is inserted into the receiving opening in the pump housing and fixed in this.
  • the ring-shaped section can be pressed into the receiving opening.
  • Such a guide section ensures—at least also—the radial centering of the pump piston.
  • a corresponding guide gap is present between the guide section and the pump piston, through which a high pressure is transmitted from the delivery chamber in the direction of the seal during operation of the piston pump.
  • the spacers have a round, preferably circular, cross-section when viewed in the axial direction.
  • the spacers can be designed in the form of axially extending nub-like projections. This keeps stresses in the material low.
  • the spacers have a rectangular cross-section when viewed in the axial direction. This is very easy to produce.
  • the seal is supported in the axial direction on a counter surface with an end facing away from the pumping chamber, and that the hydraulic gap between the seal and the counter surface is designed in such a way that when the piston pump starts to operate, the seal is laminar in the gap Flow conditions prevail, in particular that the gap has a width in the range of 5-300 pm. This can be achieved, for example, by appropriately dimensioning the distance between the mating surface and the annular section. The measure provided causes a noticeable drop in pressure in the gap at the start of operation of the piston pump.
  • the seal is made of a plastic material. Such a seal is particularly easy to produce.
  • FIG. 1 shows a longitudinal section through a piston pump
  • FIG. 2 shows an enlarged schematic longitudinal section through a region of the piston pump from FIG. 1 with a pump piston, a seal, an annular section in the form of a guide element and a retaining element;
  • Figure 3 is a perspective view of the seal of Figure 2;
  • FIG. 4 shows a schematic longitudinal section through the right-hand area of FIG. 2 to explain leakage paths
  • FIG. 5 shows a simplified hydraulic circuit diagram of the arrangement of FIG. 4
  • Figure 6 is a perspective view similar to Figure 3 of an alternative embodiment of a seal.
  • Figure 7 is a perspective view similar to Figure 3 of yet another alternative embodiment of a seal.
  • a piston pump in the form of a high-pressure fuel pump bears the reference numeral 10 overall in FIG. It usually conveys the fuel to a fuel rail to which a number of injectors are connected, which injects the fuel in the combustion chambers of the internal combustion engine.
  • the piston pump 10 comprises a controllable inlet valve 12 and an outlet valve 14 designed as a check valve, as well as a pump housing 16.
  • a receiving opening 18 for a pump piston 20 is present in this housing.
  • the pump piston 20 can be moved in the receiving opening 18 parallel to a longitudinal axis 22 of the receiving opening 18 .
  • a drive not shown in the drawing, is used for this purpose. This can be, for example, a camshaft or an eccentric shaft of the internal combustion engine.
  • the pump piston 20 is designed, for example, as a stepped piston with a section 24 with a smaller diameter and a section 26 with a larger diameter, although this is by no means mandatory.
  • the pump housing 16 can be designed as an overall rotationally symmetrical part.
  • the pump piston 20 is received in the pump housing 16 in the receiving opening 18, which is designed as a stepped blind hole with sections that each have different diameters.
  • a sleeve-shaped seal 32 made of a plastic material is arranged between the section 26 of the pump piston 20 and an inner peripheral wall 30 of the receiving opening 18 .
  • This seals directly between the pump piston 20 and the pump housing 16, and thus seals the pumping chamber 28 ("high-pressure area") located above the annular seal 32 in FIG. 1 compared to that in FIG 1 below the annular seal 32 arranged area (“low pressure area”).
  • a sleeve-shaped guide element 34 which is separate from the sleeve-shaped seal 32 and is arranged above the seal 32, which to this extent forms an annular section.
  • FIG. 1 below the seal 32, there is also a sleeve-shaped holding element 36, which is arranged in the lower region of the receiving opening 18 in FIG.
  • sleeve-shaped seal 32 rests against a mating surface (without reference number in Figure 1) of retaining element 36 that faces seal 32 in such a way that a static sealing point is formed there, which seals seal 32 from retaining element 36.
  • the retaining element 36 can be pressed into the pump housing 12 or it can be caulked in the receiving opening 18 or welded to the pump housing 16 .
  • the piston pump 10 has a further guide element 38, which is also a sleeve-shaped part and is arranged in a carrier (no reference number) which protrudes downwards from the pump housing 16 in FIG.
  • the guide element 38 also serves to guide the pump piston 20 relative to the pump housing 16.
  • the seal 32 has a first section 39 which extends in the axial direction and which is therefore overall sleeve-shaped or cylindrical. From the bottom edge of the seal 32 in the figures, that is to say the edge facing the holding element 36, a circumferential second section 40 extends radially outwards in the manner of a circumferential annular collar. In normal operation of the piston pump 10, a lower end face 42 of the seal 32 or of the radially extending section 40 in Figure 2 contacts a mating face 44 of the holding element 36 which faces upwards in Figure 1.
  • annular section 34 and seal 32 there are a plurality of flow passages 46 which at least also extend radially overall (ie allow a radial flow). In the present case, these are present on an upper edge 48 of the seal 32 in the figures.
  • the Flow passages 46 are formed between each adjacent spacer 50 as viewed in the circumferential direction. It can be seen in particular from FIG. 3 that the total extent of the flow passages 46 seen in the circumferential direction is considerably greater than the total extent of the spacers 50 seen in the circumferential direction.
  • the spacers 50 have a rectangular cross section when viewed in the axial direction. They are formed integrally with the seal 32 in the manner of axially extending projections or nubs.
  • spacers 50 are provided, distributed uniformly over the circumference. It goes without saying that more spacers can also be provided in non-illustrated embodiments.
  • R1 denotes the leakage path through the gap between the pump piston 20 and the receiving opening 18 of the pump housing 16 above the annular portion 34.
  • R2 denotes the leakage path between the seal 32 and the pump piston 20.
  • R3 denotes the leakage path through the flow passages 46 through.
  • R4 denotes the leakage path between the radial outside of the annular collar 40 and the receiving opening 18.
  • R5 denotes the leakage path through the initially existing gap between the lower end face 42 of the annular collar 40 of the seal 32 and the counter surface 44 of the retaining element 36.
  • R6 denotes the leakage path between the Holding element 36 and the pump piston 20.
  • P1 denotes the pressure that is present above the gap between the pump piston 20 and the receiving opening 18, with P1 essentially corresponding to the pressure in the pumping chamber 28 (pressure in the high-pressure area).
  • PO designates the pressure that is present below the gap between the pump piston 20 and the holding element 36, with PO essentially corresponding to the pressure in the low-pressure area.
  • P1 is > PO. This is achieved by appropriate dimensioning of R5, taking into account all tolerances and boundary conditions.
  • the gaps are to be dimensioned in such a way that there are sufficient cross sections on the leakage paths R1, R3, R4 and R6 that there is almost no throttling.
  • the gap at the throttling point R5 should be designed in such a way that laminar flow conditions prevail in it for narrow gaps. As can be seen from FIG. 5, ultimately only two relevant throttle points remain, namely the leakage paths R2 and R5.
  • the seal 32 is accommodated with a small, defined axial play between the annular section 34 and the holding element 36 .
  • a small gap between the counter surface 44 and the front surface 42 (leakage path R5).
  • this gap is in the range of 5-300 pm.
  • the seal 32 is similar to that shown in Figure 3.
  • the spacers 50 are round, namely circular, in cross-section.
  • Figure 7 shows the guide element or the annular section 34 of a further embodiment of a piston pump 10.
  • the spacers 50 are not on the seal 32, but on a lower one in the figure and to the seal 32 pointing edge of the guide element 34, specifically in the form of spacers 50 having rectangular cross sections.
  • the flow passage is provided as a channel, for example in the form of a radial or inclined radial bore, in the seal and/or the annular section.

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)

Abstract

L'invention concerne une pompe à piston (10) comprenant un piston de pompe (20), une chambre de distribution (28), un joint d'étanchéité (32) disposé en forme d'anneau autour du piston de pompe (20) et interagissant au moins par intermittence avec celui-ci, et une portion annulaire (34) qui est disposée en forme d'anneau autour du piston de pompe (20) et, vue dans la direction axiale, est disposée entre le joint d'étanchéité (32) et la chambre de distribution (28). Selon l'invention, la portion annulaire (34) est directement adjacente au joint d'étanchéité (32) et, dans la région des extrémités mutuellement adjacentes de la portion annulaire (34) et du joint d'étanchéité (32), il existe au moins un passage d'écoulement (46) ayant globalement une étendue sensiblement radiale.
PCT/EP2022/084006 2021-12-08 2022-12-01 Pompe à piston, en particulier pompe à carburant haute pression pour un moteur à combustion interne WO2023104620A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202280081383.2A CN118369508A (zh) 2021-12-08 2022-12-01 活塞泵、尤其用于内燃机的燃料高压泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021213933.7 2021-12-08
DE102021213933.7A DE102021213933A1 (de) 2021-12-08 2021-12-08 Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine

Publications (1)

Publication Number Publication Date
WO2023104620A1 true WO2023104620A1 (fr) 2023-06-15

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ID=84487786

Family Applications (1)

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PCT/EP2022/084006 WO2023104620A1 (fr) 2021-12-08 2022-12-01 Pompe à piston, en particulier pompe à carburant haute pression pour un moteur à combustion interne

Country Status (3)

Country Link
CN (1) CN118369508A (fr)
DE (1) DE102021213933A1 (fr)
WO (1) WO2023104620A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69200032T2 (de) * 1991-03-05 1994-05-26 Waertsilae Diesel Int Schmierung von Kolben einer Kraftstoffeinspritzpumpe.
DE102013200986A1 (de) * 2012-02-13 2013-08-14 Schaeffler Technologies AG & Co. KG Dichtungsanordnung
DE102014202795A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102020203652A1 (de) * 2020-03-20 2021-09-23 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017212498A1 (de) 2017-07-20 2019-01-24 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69200032T2 (de) * 1991-03-05 1994-05-26 Waertsilae Diesel Int Schmierung von Kolben einer Kraftstoffeinspritzpumpe.
DE102013200986A1 (de) * 2012-02-13 2013-08-14 Schaeffler Technologies AG & Co. KG Dichtungsanordnung
DE102014202795A1 (de) * 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102020203652A1 (de) * 2020-03-20 2021-09-23 Robert Bosch Gesellschaft mit beschränkter Haftung Kraftstoff-Hochdruckpumpe

Also Published As

Publication number Publication date
DE102021213933A1 (de) 2023-06-15
CN118369508A (zh) 2024-07-19

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