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WO2019166134A1 - Pompe à carburant haute pression à soupape de limitation de pression - Google Patents

Pompe à carburant haute pression à soupape de limitation de pression Download PDF

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Publication number
WO2019166134A1
WO2019166134A1 PCT/EP2019/050066 EP2019050066W WO2019166134A1 WO 2019166134 A1 WO2019166134 A1 WO 2019166134A1 EP 2019050066 W EP2019050066 W EP 2019050066W WO 2019166134 A1 WO2019166134 A1 WO 2019166134A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
recess
pressure
spring plate
fuel pump
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.)
Ceased
Application number
PCT/EP2019/050066
Other languages
German (de)
English (en)
Inventor
Kathrin Gerhard
Rainer Kornhaas
Matthias RIEDLE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of WO2019166134A1 publication Critical patent/WO2019166134A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • 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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0075—Stop members in valves, e.g. plates or disks limiting the movement of armature, valve or spring
    • 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
    • F02M2200/505—Adjusting spring tension by sliding spring seats
    • 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
    • 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
    • F02M2200/8092—Fuel injection apparatus manufacture, repair or assembly adjusting or calibration

Definitions

  • the invention relates to a high-pressure fuel pump according to the preamble of claim 1.
  • the invention also relates to an associated spring plate.
  • High-pressure fuel pumps for fuel systems of internal combustion engines for example for a gasoline direct injection, are known from the market.
  • Such fuel systems typically include a pressure relief valve that prevents a pressure in the high pressure accumulator from increasing too much. If the pressure in the high-pressure accumulator reaches too high a value, the pressure-limiting valve opens in the intake stroke of the high-pressure pump
  • High pressure accumulator drained into the pump room.
  • the pressure limiting valve opens when the pressure in the high pressure accumulator is so great that a pressure difference that occurs between the high pressure accumulator and the delivery chamber in the intake stroke of the high pressure pump, an opening pressure of
  • Pressure relief valve opens, fuel from the high-pressure accumulator can flow directly into an outlet region of the inlet valve.
  • the flow can in particular flow along the outside of the valve spring and then further through the outer recess in the spring plate into the outlet region of the inlet valve.
  • a discharge of the fluid directly into the delivery chamber does not take place, so that unfavorable lateral flow conditions, which can lead to an excitation of the valve spring, which in turn can lead to vibrations or increased wear, can be avoided.
  • the recess thus limits, in particular together with an inner wall of the recess, an opening through which fuel can flow.
  • valve spring is formed as a spiral spring, wherein fuel with the pressure relief valve open along the radial outer side of the valve spring and further through the recess in the
  • Substantially constant outflow surface can be provided for the volume flow, since the fluid flow flows along the radial outer side of the valve spring.
  • the recess is cylindrical.
  • the spring plate may be disc-shaped.
  • the recess of the Federtellers be provided in the radially outer region. As a result, particularly favorable flow conditions can be provided.
  • the recess is semicircular. Such a recess is particularly easy to produce and can
  • the spring plate is pressed into the recess, in particular by means of a punch.
  • the opening pressure can be adjusted via the position of the spring plate in the recess.
  • the pressure relief valve opens when the hydraulically acting force on one side of the valve element is greater than the counteracting force of the valve spring.
  • the hydraulically acting force results from the prevailing hydraulic pressure and the area on which the pressure acts. This area results from the sealing diameter.
  • this is the support ring on which the ball contacts the conical valve seat surface. Consequently, the spring plate is pressed so far into the recess until the spring force of the valve spring in conjunction with the sealing knife on the valve element corresponds to a desired opening pressure of the pressure relief valve. Since the spring force is adjustable by the present arrangement on the position of the spring plate, it is possible to form the valve seat directly in one piece with the pump housing, so that the pressing of a valve body can be omitted in the recess.
  • the spring plate has a pin which extends in the direction of the valve element.
  • This pin can taper conically, in particular in the direction of the valve element.
  • a guide for the valve spring can be provided.
  • the spring plate may in this case be formed in one piece. In this context, it is conceivable that the spring plate
  • valve spring opposite end of the valve spring is arranged on a holding piece for holding the valve element, wherein the pin has a stop for the
  • Holding piece includes.
  • a loss of the valve element for example a valve ball
  • the holding piece can in this case come into contact with the stop of the pin when the pressure-limiting valve is open at maximum, so that in particular the flow conditions in the opened pressure-limiting valve can be precisely determined and, in particular, an undesired loss of the valve element can be prevented.
  • the pin is formed by a pin arranged on the spring plate, in particular pressed therein is.
  • the press-in depth of the pin can in this case be designed to be variable in particular, so that the opening stroke of the retaining piece and thus of the pressure-limiting valve is variably adjustable.
  • a valve body is arranged, which has the valve seat.
  • the pump housing may have the valve seat. If a valve body is arranged in the recess, in particular pressed therein, the opening pressure of the pressure relief valve can be adjusted by the interaction of the Einpresstiefe of the valve body and the Einpresstiefe of the spring plate in the recess.
  • the Einpresstiefe the spring plate may be variable, the arrangement of a separate valve body omitted, so that the valve seat can be formed by the pump housing and thus a particularly simple construction and cost-effective production of
  • Pressure relief valve is available.
  • Spring plate thus has in at least one recess in the orthogonal direction to the longitudinal axis outer region, so that fuel through this
  • FIG. 1 shows a longitudinal section through a known embodiment of a
  • High-pressure fuel pump with a pump housing, a pressure relief valve, and a recess in which the pressure relief valve is accommodated;
  • Figure 2 is an enlarged detail of the recess and the
  • Figure 3 is a schematic representation of a recess and a
  • Pressure relief valve in the closed position of a high-pressure fuel pump according to a first embodiment
  • Figure 4 is a schematic representation of the illustration of Figure 3 with the pressure relief valve in the open position;
  • FIG. 6 shows a schematic arrangement for introducing the spring plate into the recess according to FIGS. 3 and 4;
  • Figure 7 is a schematic detail of a recess and a pressure relief valve in the closed position of a high-pressure fuel pump according to a second embodiment.
  • Figure 1 carries a known high-pressure fuel pump for an internal combustion engine, not shown in detail, the reference numeral 10.
  • Die High-pressure fuel pump 10 has an overall substantially
  • the high-pressure fuel pump 10 an inlet valve 14, which is also a quantity control valve at the same time, arranged in a delivery chamber 16, by a drive shaft, not shown, in a forward and
  • Herbeweg displaceable delivery piston 18, an exhaust valve 20 and a pressure relief valve 22 Herbeweg displaceable delivery piston 18, an exhaust valve 20 and a pressure relief valve 22.
  • a first channel 24 is present, which extends coaxially to the delivery chamber 16 and the delivery piston 18 and which leads from the delivery chamber 16 to a second channel 26 in the form of an overall substantially cylindrical recess which at an angle of 90 ° to first channel 24 is arranged and in which the pressure relief valve 22 is received.
  • a longitudinal axis of the pump housing 12 carries in Figure 1 a total of the reference numeral 28, a longitudinal axis of the recess 26, the reference numeral 29.
  • a pressure damper 30 is disposed in the pump housing 12.
  • the high-pressure region 32 is connected to the high-pressure fuel pump 10 via an outlet connection 34.
  • the amount of fuel that is expelled during a delivery stroke is adjusted by the solenoid-operated intake and quantity control valve 14. With an impermissible pressure in the high-pressure area, this opens
  • Pressure limiting valve 22 whereby fuel from the high-pressure region can flow into the delivery chamber 16.
  • the pressure relief valve 22 connects, as I said, in an open state, the high-pressure region 32 with the delivery chamber 16 of the high-pressure fuel pump 10.
  • the pressure relief valve 22 opens when a pressure difference between the outlet-side high-pressure region 32 and the delivery chamber 16 of the high pressure fuel pump 10 exceeds a limit.
  • the pressure limiting valve 22 is thus prevented that the pressure in the outlet-side high-pressure region 32 is unacceptably high.
  • Pressure limiting valve 22 initially includes a sleeve-like valve body 38 which is pressed into the recess 26 and in which a longitudinal direction 29 of the valve body 38 extending channel 40 is present.
  • a valve seat 42 is formed on the valve body 38, which cooperates with a valve element 44 in the form of a valve ball.
  • a holding piece 46 for holding the valve member 44 is arranged, wherein in the holding piece 46, a through hole 48 is provided, in the longitudinal direction of the holding piece 46, that is in turn parallel to the longitudinal axis 29, runs.
  • This passage opening 48 is not mandatory, but can be omitted depending on the application.
  • the holding piece 46 On the side facing away from the valve element 44 side of the holding piece 46, the holding piece 46 has a pin-like extension 50. On this a left in Figure 2, the first end portion 52 of a coil spring designed as a valve spring 54 is pushed. A right in Figure 2 right end portion 56 of the valve spring 54 of the pressure relief valve 22 is disposed in a cylindrical end portion 58 of the recess 26 on the pump housing 12.
  • the recess 26 extends according to the present embodiments of Figures 3 to 7 through the pump housing to an outlet portion 60 of the inlet valve 14. Further, no connection channel 24 between the recess 26 and the delivery chamber 16 more available.
  • the recess 26 is cylindrical.
  • the valve seat 42 is formed in one piece from the pump housing 12. Furthermore, the channel 40 is also introduced directly into the pump housing 12. In the recess 26, a spring plate 62 is pressed. In the orthogonal direction 63 to the longitudinal axis 29 62 four recesses 64 are on the outer edge of the spring plate intended. These recesses are semi-circular introduced as a half-cylinder in the spring plate 62. As can be seen particularly clearly from FIG. 5, the spring plate has, in addition to the disc-shaped spring plate section 65, a pin 66 extending in the direction of the valve element 44. This tapers conically in the direction of the valve element 44. Between the pin 66 and the spring plate portion 65 a constriction 68 is present.
  • the spring plate 62 can be pressed by means of a punch 70 by applying a force indicated by the arrow F in the recess 26.
  • the valve spring 54 can be compressed, so that thereby the restoring force on the valve element 44 is adjustable. This can ultimately be the opening pressure of the
  • Pressure relief valve 22 can be adjusted.
  • the pin 66 has a stop 72 on its free end lying in the direction of the valve element 44.
  • the holding piece 46 has a counter-abutment 74 at its end remote from the valve element 44. If that
  • Pressure relief valve 22 is open at the maximum, so the counter-stop 74 of the retaining piece 46 abuts against the stop 72 of the spring plate 62. A further opening of the pressure limiting valve 22 is thus no longer possible.
  • the stop can be prevented in particular that the valve element 44 is undesirably lost and, for example, between the valve body 38 (embodiment of Figure 7) and the retaining piece 46 and the pump housing 12 (embodiment according to Figures 3 to 6) and the holding piece 46 wedged.
  • Valve body 38 which is pressed into the recess 26 is formed.
  • the valve seat 42 as in the embodiment according to FIGS. 3 to 6, could of course also be formed here by the pump housing 12.
  • the spring plate 62 is constructed in two parts and initially comprises the one also shown in the first embodiment
  • a cylindrical pin 82 is pressed into the disc-shaped spring plate portion 65 of the spring plate 62.
  • the penetration depth of the pin 82 into the recess 26 can be set variably, so that in this way the position of the stopper 72 is variable and thereby in a particularly simple manner the stop position of the counter-stop 74 when open
  • Pressure relief valve 22 can be adjusted.
  • Valve spring 54 between the valve spring 54 and an inner side 78, which the
  • the recesses 64 thus represent breakthroughs, on the one hand from the spring plate 62 and the other part of the Inside 78 of the recess 26 are limited.

Landscapes

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

Abstract

L'invention concerne une pompe à carburant haute pression (10) pour un système d'injection de carburant d'un moteur à combustion interne. La pompe est pourvue d'un corps (12), d'une soupape d'admission (14) et d'une soupape de limitation de pression (22), laquelle est logée dans le corps (12) de la pompe dans un creux (26) s'étendant le long d'un axe longitudinal (29). L'invention est caractérisée en ce que le creux (26) s'étend jusqu'à une zone de sortie (60) de la soupape d'admission (14), une coupelle (62) de ressort étant disposée dans le creux (26). Un ressort (54) de soupape, qui sollicite un élément (44) de soupape contre un siège (42) de soupape, est fixé sur la coupelle (62) de ressort, et la coupelle (62) de ressort présente sur sa zone extérieure dans la direction (63) perpendiculaire à l'axe longitudinal (29) au moins un évidement (64), de sorte que le carburant peut s'écouler dans la zone de sortie (60) en passant par l'évidement (64).
PCT/EP2019/050066 2018-03-02 2019-01-03 Pompe à carburant haute pression à soupape de limitation de pression Ceased WO2019166134A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018203154.1A DE102018203154A1 (de) 2018-03-02 2018-03-02 Kraftstoff-Hochdruckpumpe mit Druckbegrenzungsventil
DE102018203154.1 2018-03-02

Publications (1)

Publication Number Publication Date
WO2019166134A1 true WO2019166134A1 (fr) 2019-09-06

Family

ID=65003387

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/050066 Ceased WO2019166134A1 (fr) 2018-03-02 2019-01-03 Pompe à carburant haute pression à soupape de limitation de pression

Country Status (2)

Country Link
DE (1) DE102018203154A1 (fr)
WO (1) WO2019166134A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114630955A (zh) * 2019-10-23 2022-06-14 罗伯特·博世有限公司 燃料高压泵

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050205065A1 (en) * 2004-03-17 2005-09-22 Helmut Rembold High-pressure fuel pump with a pressure relief valve
CN102200193A (zh) * 2010-05-24 2011-09-28 浙江万向精工有限公司 一种柱塞泵单向阀
EP2497939A1 (fr) * 2011-03-08 2012-09-12 Hitachi Automotive Systems, Ltd. Pompe d'alimentation en carburant haute pression

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20050205065A1 (en) * 2004-03-17 2005-09-22 Helmut Rembold High-pressure fuel pump with a pressure relief valve
CN102200193A (zh) * 2010-05-24 2011-09-28 浙江万向精工有限公司 一种柱塞泵单向阀
EP2497939A1 (fr) * 2011-03-08 2012-09-12 Hitachi Automotive Systems, Ltd. Pompe d'alimentation en carburant haute pression

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114630955A (zh) * 2019-10-23 2022-06-14 罗伯特·博世有限公司 燃料高压泵

Also Published As

Publication number Publication date
DE102018203154A1 (de) 2019-09-05

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