WO2022218850A1 - Pompe à carburant haute-pression - Google Patents

Pompe à carburant haute-pression Download PDF

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Publication number
WO2022218850A1
WO2022218850A1 PCT/EP2022/059403 EP2022059403W WO2022218850A1 WO 2022218850 A1 WO2022218850 A1 WO 2022218850A1 EP 2022059403 W EP2022059403 W EP 2022059403W WO 2022218850 A1 WO2022218850 A1 WO 2022218850A1
Authority
WO
WIPO (PCT)
Prior art keywords
spiral spring
pressure
valve
fuel pump
pressure fuel
Prior art date
Application number
PCT/EP2022/059403
Other languages
German (de)
English (en)
Inventor
Stephan Wehr
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 CN202280028451.9A priority Critical patent/CN117120713A/zh
Publication of WO2022218850A1 publication Critical patent/WO2022218850A1/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
    • F02M59/46—Valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005—Pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0054—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps

Definitions

  • High-pressure fuel pumps with the features of the preamble of claim 1 are already known from DE 102004 013307 A1, DE 102019202 271 A1, DE 102019 200 025 A1, DE 102018218919 A1 and DE102018209033 A1 of the applicant.
  • the present invention is initially based on the knowledge that in continuous operation of such high-pressure fuel pumps, wear phenomena that impair the function can occur on the valve element and/or on the valve body of the pressure-limiting valve, which are based on friction between the valve element and the valve body in the area of the valve seat. In particular, wear can be accompanied by a drop in the opening pressure of the pressure-limiting valve.
  • the high-pressure fuel pump is then only able to compress fuel to a high pressure to a limited extent.
  • the present invention is based on the desire for a solution to the above-mentioned problem which, in comparison to the conventional product, does not cause any additional costs or does not require additional components and assembly steps.
  • the last turns of the spiral spring pointing towards the valve seat are arranged in a block, for example.
  • the measure according to the invention dampens both longitudinal vibrations of the spiral spring (in the axial direction) and transverse vibrations (perpendicular to the axial direction) of the spiral spring in its end region pointing towards the valve seat. This reduces the transmission of vibrations of the spiral spring to the holding element. As a result, the friction occurring between the valve element and the valve body is reduced, and thus the wear. The function of the pressure-limiting valve and thus also of the high-pressure fuel pump is therefore unimpaired for longer.
  • the measure shown is essentially neutral compared to the use of a conventional spiral spring, the turns of which are all spaced apart from one another.
  • the number of windings of the spiral spring that lie against one another is in particular at least as large as the quotient of the axial extension of the radially inner area of the holding body protruding from the radially outer area divided by the axial extension of a single winding of the spiral spring.
  • the number of dead turns can thus be 2 or more than 2 or 3 or more than 3.
  • the quotient of the number of turns of the spiral spring that are in contact with one another and pointing towards the valve seat and the total number of turns of the spiral spring is in the interval from 0.25 to 0.4.
  • the axial end of the spiral spring pointing to the valve seat, in particular the last end to the valve seat pointing turn is ground plane perpendicular to the axial direction.
  • the spiral spring when the pressure-limiting valve is closed, the same number of windings of the spiral spring rest against one another at both axial ends of the spiral spring, the spiral spring has in particular two essentially identically designed axial ends. It can easily be installed in both orientations in the pressure-limiting valve, with the effects described above occurring in both cases.
  • the high-pressure fuel pump according to the invention can therefore be produced more reliably and more easily.
  • Figure 1 shows a longitudinal section through a high-pressure fuel pump according to the invention
  • FIG 2 is an enlargement of the pressure relief valve from Figure 1,
  • Figure 3 shows a conventional pressure relief valve
  • FIG. 4 shows a pressure-limiting valve according to a further improvement.
  • a high-pressure fuel pump for an internal combustion engine bears the reference numeral 10.
  • the high-pressure fuel pump 10 has an overall essentially cylindrical pump housing 12, in or on which the essential components of the high-pressure fuel pump 10 are arranged.
  • the high-pressure fuel pump 10 has a fuel connection 11, an inlet and quantity control valve 14, a delivery piston 18 which is arranged in a delivery chamber 16 and can be moved back and forth by a drive shaft (not shown), an outlet valve 20 and a pressure-limiting valve 22.
  • first cylindrical channel 24 which extends coaxially to the delivery chamber 16 and to the delivery piston 18 and which leads from the delivery chamber 16 to a second cylindrical channel 26 which is arranged at an angle of 90° to the first channel 24 and in which the pressure relief valve 22 is accommodated.
  • a longitudinal axis of the pump housing 12 bears the reference number 28 in FIG. 1, and a longitudinal axis of the second cylindrical channel 26 bears the reference number 29.
  • the longitudinal axis 29 of the second cylindrical channel 26 runs in the axial direction, to which reference is made within the scope of the invention with regard to the pressure relief valve and its subcomponents.
  • the delivery piston 18 sucks in a fuel, for example a fuel such as gasoline, via the inlet and quantity control valve 14 into the delivery chamber 16 during an intake stroke.
  • a fuel for example a fuel such as gasoline
  • the fuel in the delivery chamber 16 is compressed and ejected via the outlet valve 20, for example, into a high-pressure area 32, for example to a fuel collection line ("rail"), where the fuel is stored under high pressure.
  • the high-pressure region 32 is connected to the high-pressure fuel pump 10 via an outlet 34 designed as an outlet connection.
  • the amount of fuel that is ejected during a delivery stroke is set by the electromagnetically actuated inlet and quantity control valve 14 .
  • the pressure-limiting valve 22 connects the high-pressure area 32 to the pumping chamber 16 of the high-pressure fuel pump 10 when it is open.
  • the pressure-limiting valve 22 opens when there is a pressure difference between the high-pressure area 32 on the outlet side and the pumping chamber 16 of the high-pressure fuel pump 10 exceeds a limit.
  • the pressure-limiting valve 22 thus prevents the pressure in the high-pressure area 32 on the outlet side from being impermissibly high.
  • the opening pressure of the pressure-limiting valve 22 is selected accordingly and ensured over the service life of the high-pressure fuel pump.
  • the pressure-limiting valve 22 initially includes a sleeve-like valve seat body 38 which is pressed into the cylindrical channel 26 .
  • a conical valve seat 42 is formed on the right-hand side of valve seat body 38 in FIG.
  • the pressure-limiting valve 22 also includes a spiral spring 52 supported on the pump housing 12, which presses the retaining element 46 against the valve element 44 in the closing direction.
  • the holding element 46 On the side facing away from the valve element 44, the holding element 46 has, radially on the outside, an annular shoulder 464 on which the spiral spring 52 rests. For planar contact of the spiral spring 52 on the annular shoulder 464, it is provided that the last turn 521 of the spiral spring 52 pointing towards the valve seat 42 is ground plane perpendicular to the axial direction.
  • the valve body 46 has, on the side facing away from the valve element 44 , radially inwards, a pin 465 pointing away from the valve element 44 , which is received by the outer windings 521 of the spiral spring 52 pointing towards the valve element 44 .
  • turns 521 of the spiral spring 52 rest against one another along the axial extension e, in which the pin 465 of the retaining element 46 is accommodated in the spiral spring 52, i.e. they are in a block or are dead turns of the spiral spring 52 .
  • the six further turns 52f of the spiral spring 52 in the example are spaced apart from one another, so that they can oscillate in the longitudinal and transverse directions.
  • FIG. 3 shows a conventional pressure-limiting valve 22h of a conventional high-pressure fuel pump, as is known, for example, from the prior art mentioned at the outset.
  • the conventional pressure relief valve 22h all turns 521h of the spiral spring 52h are spaced apart from one another.
  • longitudinal and transverse vibrations are shown, to which the coil spring 52h through the is excited by the volume flow that prevails in the cylindrical channel 26h and by cavitation that may occur there.
  • these vibrations 77h continue into the area in which the spiral spring 52h is in contact with the holding element 46h and are transmitted from there via the valve element 44h to the valve seat 42h.
  • Figure 4 shows a pressure relief valve 22 according to a further improvement. It is characterized by the fact that when the pressure-limiting valve 22 is closed, the same number of windings 521 of the spiral spring 52 rest against one another at both axial ends of the spiral spring 52 .

Landscapes

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

Abstract

L'invention concerne une pompe à carburant haute-pression (10) comprenant une soupape de limitation de pression (22). La soupape de limitation de pression (22) est conçue de manière à avoir un corps de siège de soupape (38) sur lequel est formé un siège de soupape conique (42). La soupape de limitation de pression (22) comporte un élément de soupape (44) qui présente une forme conique et qui vient en contact d'étanchéité avec le siège de soupape (42), l'élément de soupape (44) étant poussé dans la direction de fermeture par un élément de maintien (46), et l'élément de maintien (46) étant poussé dans la direction de fermeture par un ressort en spirale (52). Le ressort en spirale (52) est supporté sur un boîtier de la soupape de limitation de pression (22) ou sur le carter de pompe (12), et le ressort en spirale (52) est supporté sur une région radialement extérieure (464) de l'élément de maintien (46), ledit ressort hélicoïdal (46) recevant une région radialement intérieure (465) de l'élément de maintien (46). Selon l'invention, les enroulements (521) du ressort en spirale (52) reposent les uns contre les autres le long de l'extension axiale (e) dans laquelle la zone radialement intérieure (465) de l'élément de maintien (46) est logée dans le ressort en spirale (52) lorsque la soupape de limitation de pression (22) est fermée.
PCT/EP2022/059403 2021-04-14 2022-04-08 Pompe à carburant haute-pression WO2022218850A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202280028451.9A CN117120713A (zh) 2021-04-14 2022-04-08 燃料高压泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102021203663.5A DE102021203663A1 (de) 2021-04-14 2021-04-14 Kraftstoff-Hochdruckpumpe
DE102021203663.5 2021-04-14

Publications (1)

Publication Number Publication Date
WO2022218850A1 true WO2022218850A1 (fr) 2022-10-20

Family

ID=81325583

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2022/059403 WO2022218850A1 (fr) 2021-04-14 2022-04-08 Pompe à carburant haute-pression

Country Status (3)

Country Link
CN (1) CN117120713A (fr)
DE (1) DE102021203663A1 (fr)
WO (1) WO2022218850A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1500855A1 (fr) * 2003-07-22 2005-01-26 TI Group Automotive Systems, L.L.C. Vanne de régulation de la pression
DE102004013307A1 (de) 2004-03-17 2005-09-29 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
WO2015173013A1 (fr) * 2014-05-12 2015-11-19 Continental Automotive Gmbh Procédé de fabrication d'une soupape de limitation de pression, soupape de limitation de pression, et composant pour système d'injection de carburant
DE102016213333A1 (de) * 2016-07-21 2018-01-25 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
DE102018209033A1 (de) 2018-06-07 2019-12-12 Robert Bosch Gmbh Kraftstoff-Hochdruckkolbenpumpe
DE102018218919A1 (de) 2018-11-06 2020-05-07 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
DE102019200025A1 (de) 2019-01-03 2020-07-09 Robert Bosch Gmbh Druckbegrenzungsventil für eine Kraftstoff-Hochdruckpumpe
DE102019202271A1 (de) 2019-02-20 2020-08-20 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1500855A1 (fr) * 2003-07-22 2005-01-26 TI Group Automotive Systems, L.L.C. Vanne de régulation de la pression
DE102004013307A1 (de) 2004-03-17 2005-09-29 Robert Bosch Gmbh Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
WO2015173013A1 (fr) * 2014-05-12 2015-11-19 Continental Automotive Gmbh Procédé de fabrication d'une soupape de limitation de pression, soupape de limitation de pression, et composant pour système d'injection de carburant
DE102016213333A1 (de) * 2016-07-21 2018-01-25 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
DE102018209033A1 (de) 2018-06-07 2019-12-12 Robert Bosch Gmbh Kraftstoff-Hochdruckkolbenpumpe
DE102018218919A1 (de) 2018-11-06 2020-05-07 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
DE102019200025A1 (de) 2019-01-03 2020-07-09 Robert Bosch Gmbh Druckbegrenzungsventil für eine Kraftstoff-Hochdruckpumpe
DE102019202271A1 (de) 2019-02-20 2020-08-20 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe

Also Published As

Publication number Publication date
DE102021203663A1 (de) 2022-10-20
CN117120713A (zh) 2023-11-24

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