WO2019197065A1 - Soupape de limitation de pression - Google Patents

Soupape de limitation de pression Download PDF

Info

Publication number
WO2019197065A1
WO2019197065A1 PCT/EP2019/053008 EP2019053008W WO2019197065A1 WO 2019197065 A1 WO2019197065 A1 WO 2019197065A1 EP 2019053008 W EP2019053008 W EP 2019053008W WO 2019197065 A1 WO2019197065 A1 WO 2019197065A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
pressure relief
holding piece
relief valve
Prior art date
Application number
PCT/EP2019/053008
Other languages
German (de)
English (en)
Inventor
Martin Bechle
Klaus Lang
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 WO2019197065A1 publication Critical patent/WO2019197065A1/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
    • 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
    • F02M63/0033—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036—Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls
    • F16K15/044—Check valves with guided rigid valve members shaped as balls spring-loaded
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0406—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of balls
    • 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
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • 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
    • F02M2200/9038—Coatings
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • F02M63/0235—Means for varying pressure in common rails by bleeding fuel pressure
    • F02M63/0245—Means for varying pressure in common rails by bleeding fuel pressure between the high pressure pump and the common rail

Definitions

  • the invention relates to a pressure relief valve according to the preamble of claim 1.
  • the invention also relates to an associated high-pressure fuel pump.
  • High-pressure fuel pumps for fuel systems of internal combustion engines for example for a gasoline direct injection, are known from the market.
  • fuel is conveyed from a fuel tank by means of a prefeed pump and the mechanically driven high-pressure pump under high pressure into a high-pressure accumulator ("rail").
  • 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 sucked into the delivery chamber.
  • 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
  • the invention has the advantage that due to the point-like connection between the loading element and the valve element, the introduction or transmission of torque from
  • valve element directly or in particular also indirectly via the contact point on
  • the invention is based on the following considerations: The fact that high-pressure fuel pumps are usually mounted directly on the internal combustion engine, they are exposed to high vibrational acceleration excitations.
  • Beaufschlagungselement can thereby be excited axially and / or radially to vibrations, which may be particularly pronounced in particular in the eigenmodes (resonance points) of the biasing element.
  • this dynamic excitation can lead to a deformation along the bending line of the eigenmodes.
  • connection between the loading element and the valve element is punctiform or at least essentially point-shaped, no or no relevant torque is introduced from the loading element into the valve element.
  • an undesirable movement of the valve element can be prevented at the valve seat.
  • a rotation of the valve element can be prevented.
  • the invention reduces the wear between the valve seat and the valve element, which over the life of the
  • Pressure relief valve leads to a smaller change in the opening pressure and to an improved tightness. Overall, costs can be saved because the service life of the pressure relief valve can be extended. Also, a relatively inexpensive production is possible.
  • Beauftschungselement arranged a holding piece on which the
  • Beauftschungselement is fixed, wherein the holding piece has a contact surface for conditioning of the valve element, and wherein the contact surface of the
  • the valve element thus touches the holding piece. Due to the movement of the holding piece relative to the valve element, the contact point between the valve element and holding piece can move. Nevertheless, the contact point remains punctiform or at least substantially punctiform. As a result, the wear between the valve element and
  • Valve seat and between the valve element and holding piece are reduced in an advantageous manner ..
  • the contact surface comprises an orthogonal to the opening direction extending flat surface. This contact surface is thus touched by the valve element at the contact point.
  • the holding piece can still move relative to the valve element, for example
  • Recess may be introduced in the form of a Kugelsegements, so that in this way the concave surface is formed.
  • valve element in particular in the case of a ball-shaped valve element, rolling along the valve element. This can prevent that a torque is introduced into the valve element. Nevertheless, a movement of the holding piece is made possible relative to the valve element.
  • the valve element is designed as a valve ball.
  • the curvature of the valve ball can be greater than the curvature of the contact surface. The curvature is the reciprocal of the radius. As a result, the holding piece can roll on the valve element.
  • the contact surface is formed convex seen from the valve element. Consequently, the holding piece may have a bulge in the direction of the valve seat. This bulge may be formed in particular in the form of a convex spherical segment. The curvature of this ball segment can in turn be greater than the curvature of a
  • Valve ball formed valve element The holding piece can move relative to the valve element rolling.
  • the contact surface is at least partially coated.
  • the holding piece comprises a hardening element, wherein the hardening element in any case comprises a portion of the contact surface. As a result, a particularly wear-resistant pressure relief valve is provided.
  • the holding piece has an edge surface orthogonal to the opening direction, which has an arcuate, convex outer contour. Consequently, when the holding piece against the
  • the holding piece can come over the edge surface on an inner side of a recess to the plant in which the
  • Pressure relief valve is arranged. This contact can also be punctiform. This can also reduce the wear of the
  • Pressure relief valve can be reduced and thus the service life can be increased.
  • the edge surface has a recess extending in the opening direction for fluid outflow.
  • a continuous and secure fluid outflow can also be provided when the holding piece is displaced in the open position of the pressure limiting valve from a neutral position relative to the valve element in a Auslenklage, in particular the edge surface comes to rest on the inside of the recess for the pressure relief valve.
  • the pressure relief valve can open to a pumping chamber and be arranged fluidly between the pumping chamber and a high-pressure accumulator.
  • Pressure relief valve opens at low pressures and thus the
  • the pressure relief valve opens to an antechamber of the inlet valve and is thus arranged fluidly between the antechamber of the inlet valve and, for example, the high-pressure accumulator.
  • FIG. 1 shows a longitudinal section through a first embodiment of a high-pressure fuel pump with a pump housing, a
  • Pressure relief valve according to a first embodiment, 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 view similar to Figure 2 of a portion of a
  • FIG. 4 shows a representation of the pressure limiting valve according to FIG. 3 during operation
  • Figure 5 is a view similar to Figure 2 of a portion of a
  • a high-pressure fuel pump for an internal combustion engine not shown in detail bears the reference numeral 10.
  • the high-pressure fuel pump 10 has an overall substantially 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 an inlet and quantity control valve 14, an arranged in a delivery chamber 16, displaceable by a drive shaft not shown in a reciprocating motion 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 limiting 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 a Exceeds limit. By the pressure limiting valve 22 is thus prevented that the pressure in the outlet-side high-pressure region 32 is unacceptably high.
  • Pressure relief valve 22 initially includes a sleeve-like valve seat body 38 which is pressed into the recess 26 and in which a longitudinal direction 29 of the valve seat body 38 extending channel 40 is present.
  • a valve seat 42 is formed on the valve seat body 38 which cooperates with a valve element 44 in the form of a valve ball.
  • Valve element 44 is a cross-sectionally T-shaped holding piece 46 is arranged.
  • the holding piece 46 On the side of the holding piece 46 facing away from the valve element 44, the holding piece 46 has a pin-like extension 48. On this one left in the figure, the first end portion 50 of a trained as a spiral spring
  • Pressure limiting valve 22 is arranged in a cylindrical end region 54 of the recess 26.
  • valve body 38 and the retaining piece 46 are rotationally symmetrical about a central longitudinal axis 56 which is connected to the longitudinal axis 29 of the
  • Opening direction 58 This direction is parallel to the longitudinal axis 29 and the central longitudinal axis 56th
  • the holding piece 46 has a
  • abutment surface 60 is exemplarily designed as a flat surface 61 that extends orthogonally to opening direction 58.
  • the contact surface 60 contacts the valve element 44 at a point-shaped contact point 62.
  • the point-shaped contact point 62 is located on the
  • Contact surface 60 is not flat, but seen from the valve element 44 is concave. Consequently, on the valve element 44 facing side of the holding piece 46 has a recess 64 is introduced in the form of a spherical segment.
  • the valve element 44 in this case has a radius r1, wherein the center of the valve element 44 is in the closed position on the longitudinal axis 29.
  • the radius r2 associated with the spherical segment-shaped recess 64 is greater than the radius r1.
  • the radius r2 is greater than the radius r1, so that the valve element 44 has a greater curvature than the spherical segment-shaped recess 64.
  • the radius r1 can be between 0.5 and 1, 5 mm.
  • the radius r2 can be between 0.6 and 5 mm.
  • the holding piece 46 viewed from the valve element 44, has a convex contact surface 60. Consequently, the holding piece 46 is bulged out to the valve element 44 and is thus formed as a whole mushroom-shaped.
  • the bulge 66 has the shape of a Kugelsegements. This spherical segment can have a radius r3.
  • the center of an imaginary ball to this ball segment is also in the rest position on the longitudinal axis 29.
  • the radius r3 is greater than the radius r1 of the valve element, so that in total the curvature of
  • Valve element 44 is greater than the curvature of the contact surface 60th
  • the abutment surface 60 of the embodiment shown in FIG. 5 is formed by a hardening element 68 which projects into a recess 70 in the region of the bulge 66 of the retaining piece 46 was introduced.
  • the region of the holding piece 46 surrounding the hardening element 68 may be made of a softer material and thus
  • the holding piece 46 has an edge surface 72, which has an arcuate outer contour that is convex when viewed from the outside. This edge surface extends over the entire circumference of the holding piece 46. However, at least one recess 74 is introduced into the edge surface 72 in a peripheral region.
  • the mode of operation of the pressure limiting valve 22 is explained below by way of example, in particular, with reference to FIG. 4: Due to the fact that the high-pressure fuel pump 10 can be mounted directly on the internal combustion engine, high vibration acceleration excitations can occur. As a result, the biasing element 52 can be excited to oscillations, which can be particularly pronounced, in particular in the eigenmodes. This excitation can lead to a deformation along a bending line 76 of the loading element 52. The vibration of the
  • Beauftschungselements 52 may in this case be sinusoidal in particular.
  • Vibrational excitations may additionally or alternatively also be effected by the operation of the high-pressure fuel pump 10 itself, for example by cyclically impressing flow forces on the biasing element 52 in the conveying space 16 during conveying and / or suction.
  • the wear can be further advantageously reduced by making the edge surface 72 arcuate. Consequently, if the holding piece 46 comes to bear against the inner wall 77 of the recess 26, in turn results in an ideally punctiform contact point. Thus, the wear can also be reduced by the arcuate design. As a result of the fact that at least one recess 74 is provided, a reliable fluid removal can still be provided.

Landscapes

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

Abstract

Soupape de limitation de pression (22), comprenant un élément de soupape (44) et un élément de sollicitation (52) qui sollicite l'élément de soupape (44) contre un siège de soupape (42) dans le sens contraire d'un sens d'ouverture (58), l'élément de soupape (44) étant disposé sur l'élément de sollicitation (52) par le biais d'un endroit de contact (62) ponctuel ou sensiblement ponctuel.
PCT/EP2019/053008 2018-04-12 2019-02-07 Soupape de limitation de pression WO2019197065A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018205599.8 2018-04-12
DE102018205599.8A DE102018205599A1 (de) 2018-04-12 2018-04-12 Druckbegrenzungsventil

Publications (1)

Publication Number Publication Date
WO2019197065A1 true WO2019197065A1 (fr) 2019-10-17

Family

ID=65363290

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2019/053008 WO2019197065A1 (fr) 2018-04-12 2019-02-07 Soupape de limitation de pression

Country Status (2)

Country Link
DE (1) DE102018205599A1 (fr)
WO (1) WO2019197065A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006093596A1 (fr) * 2005-02-28 2006-09-08 Caterpillar Inc. Soupape de relâchement de pression
DE102013202588A1 (de) * 2012-07-04 2014-01-09 Continental Teves Ag & Co. Ohg Ventilbaugruppe
US20140116387A1 (en) * 2012-10-25 2014-05-01 Caterpillar Inc. Pressure relief valve for common rail fuel system
EP2728164A1 (fr) * 2012-10-30 2014-05-07 Delphi International Operations Luxembourg S.à r.l. Agencement de soupape
DE102012111703A1 (de) * 2012-12-03 2014-06-05 Zf Lenksysteme Gmbh Druckbegrenzungsventil und Verfahren zur Einstellung einer Vorspannkraft eines Druckbegrenzungsventiles
DE102013213419A1 (de) * 2013-07-09 2015-01-15 Robert Bosch Gmbh Neuartige Stößelspitzen-Geometrie für ein Druckregelventil
US20150300339A1 (en) * 2014-04-21 2015-10-22 Stanadyne Llc Pressure Relief Valve For Single Plunger Fuel Pump

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006093596A1 (fr) * 2005-02-28 2006-09-08 Caterpillar Inc. Soupape de relâchement de pression
DE102013202588A1 (de) * 2012-07-04 2014-01-09 Continental Teves Ag & Co. Ohg Ventilbaugruppe
US20140116387A1 (en) * 2012-10-25 2014-05-01 Caterpillar Inc. Pressure relief valve for common rail fuel system
EP2728164A1 (fr) * 2012-10-30 2014-05-07 Delphi International Operations Luxembourg S.à r.l. Agencement de soupape
DE102012111703A1 (de) * 2012-12-03 2014-06-05 Zf Lenksysteme Gmbh Druckbegrenzungsventil und Verfahren zur Einstellung einer Vorspannkraft eines Druckbegrenzungsventiles
DE102013213419A1 (de) * 2013-07-09 2015-01-15 Robert Bosch Gmbh Neuartige Stößelspitzen-Geometrie für ein Druckregelventil
US20150300339A1 (en) * 2014-04-21 2015-10-22 Stanadyne Llc Pressure Relief Valve For Single Plunger Fuel Pump

Also Published As

Publication number Publication date
DE102018205599A1 (de) 2019-10-17

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