WO2019166136A1 - Soupape de limitation de pression - Google Patents

Soupape de limitation de pression Download PDF

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Publication number
WO2019166136A1
WO2019166136A1 PCT/EP2019/050073 EP2019050073W WO2019166136A1 WO 2019166136 A1 WO2019166136 A1 WO 2019166136A1 EP 2019050073 W EP2019050073 W EP 2019050073W WO 2019166136 A1 WO2019166136 A1 WO 2019166136A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
angle
seat surface
valve seat
Prior art date
Application number
PCT/EP2019/050073
Other languages
German (de)
English (en)
Inventor
Sebastian Vietze
Michael Kleindl
Bernd Berghaenel
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
Publication of WO2019166136A1 publication Critical patent/WO2019166136A1/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
    • F02M63/0033—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
    • 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
    • F16K1/00—Lift valves or globe valves, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces
    • F16K1/32—Details
    • F16K1/34—Cutting-off parts, e.g. valve members, seats
    • F16K1/42—Valve seats
    • 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
    • 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
    • F16K17/0466—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 with a special seating surface

Definitions

  • the invention relates to a pressure relief valve according to the preamble of claim 1.
  • the invention also relates to a high-pressure fuel pump with an associated pressure relief valve.
  • 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 pressure relief valve opens when the hydraulically acting force on one side of the valve element is greater than the counteracting Force of the loading element.
  • 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. This support ring and thus the
  • Sealing diameter may change over the life due to wear.
  • the support ring can become more and more of an annular surface, so that the acting sealing diameter shifts within this annular surface. This can lead to a change in the opening pressure, since the area of the valve element on which the pressure can act can change.
  • an increase or decrease in the opening pressure is conceivable. In particular, it is critical to increase the opening pressure by reducing the
  • the valve element may be formed in particular spherical.
  • the first tubular portion may be formed in particular as a throttle bore.
  • the valve body can be formed rotationally symmetrical overall in particular about the central longitudinal axis.
  • the second tubular portion may be substantially the diameter of a spherical valve member
  • the second tubular section can therefore
  • valve element in particular serve as a guide for the valve element.
  • the width may correspond to a developable due to wear ring surface, or a significant slowdown of the wear width increase can be achieved. As a result, the possible change in the opening pressure is limited or slowed down. This can be prevented in particular that the
  • the minimum diameter of the wear width over the life can not be smaller than the diameter of the valve body at the transition from the transition surface to the valve seat surface.
  • Sealing diameter (maximum Ventilelementauflagering) can be achieved.
  • the maximum sealing diameter over the service life can in this case be, in particular, at the transition from the valve seat surface to the second transition surface.
  • the angles ⁇ and g can be different and thus differ in the effectiveness against the wear width increase and robustness.
  • the angle g can be 0 °, so that the first
  • Transition surface extends in the opening direction parallel to the central longitudinal axis, wherein between the first portion and the first transition surface, a first intermediate surface is present. By the transition surface extends parallel to the central longitudinal axis in the opening direction, the inner
  • Wear diameter are set.
  • the contact point or the contact ring may lie, for example, in the middle of the valve seat surface. Due to wear, the valve ball can shift in the direction of the closing direction. The diameter of the However, bearing rings can not become smaller over the service life than the diameter of the first transition surface.
  • the first intermediate surface extends at an angle m to the central longitudinal axis.
  • Throttle bore diameter may be a conical in
  • the angle m is 90 °, so that a step is formed between the first portion and the valve seat surface.
  • Intermediate surface can thus be formed as a circular ring.
  • a right-angled step can be formed.
  • This step can have an extent along the central longitudinal axis of, for example, 1 to 3 mm, in particular 2 mm, while the extent orthogonal to the central longitudinal axis can be, for example, 0.001 to 0.1 mm, in particular 0.01 mm.
  • the angle ⁇ is between 90 ° and 180 °.
  • the maximum outer wear diameter can be reduced.
  • angles between 135 and 180 ° are advantageous.
  • angle ⁇ is 180 °, so that the second transition surface in one of the opening direction opposite
  • Closing direction extends parallel to the central longitudinal axis. As a result, a maximum limitation of the maximum sealing ring over the lifetime can be achieved.
  • Transition surface can not extend over the life and thus the diameter of the valve seat surface at the transition to the transition surface represent the maximum sealing ring diameter.
  • a second intermediate surface is present, which extends in particular orthogonal to the central longitudinal axis.
  • the intermediate surface thus forms in particular an annular surface. This surface may merge into the second tubular section.
  • valve element is spherical, wherein the contact point of the valve element before the use of the
  • the diameter of the first transition surface may correspond to the minimum sealing diameter, which in particular does not change over the life of the pressure relief valve, so that the risk of increasing the opening pressure over the lifetime can be minimized.
  • the pressure limiting valve can open to a pumping chamber.
  • the pressure limiting valve can also be arranged fluidically between the delivery chamber and a high-pressure accumulator.
  • the risk of high pressures in the rail can be minimized, in which a risk of bursting or a risk that injectors can not open, can be reduced. Furthermore, it can be avoided in particular that the pressure relief valve opens at too low pressures and thus the system pressure in the rail can no longer be achieved or maintained.
  • Figure 1 shows a longitudinal section through a first embodiment of a high pressure fuel pump with a pump housing, a known pressure relief valve, and a recess in which the
  • Figure 2 is an enlarged detail of the recess and the
  • FIG. 3 shows a detail III from FIG. 2;
  • FIG. 4 shows a section of a pressure-limiting valve according to a first embodiment
  • FIG. 5 depicts a section of a pressure-limiting valve according to a second embodiment
  • Figure 6 shows a portion of a pressure relief valve according to a third embodiment
  • Figure 7 shows a portion of a pressure relief valve according to a fourth embodiment.
  • 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 intake / quantity control valve 14, one in one
  • Delivery chamber 16 arranged, 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 in FIG. 1 bears the reference numeral 28 as a whole.
  • a pump housing 12 is provided in FIG. 1 at the top, a pump housing 12 is provided
  • Pressure damper 30 is arranged.
  • 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 limiting valve 22 first includes a sleeve-like valve body 38 which is pressed into the recess 26 and in which a longitudinal direction of the valve seat body 38 extending channel 40 is present.
  • the valve body 38 has a central longitudinal axis 29 and is a total of rotationally symmetrical about the central longitudinal axis 29.
  • a valve seat 42 is formed, which cooperates with a valve element 44 in the form of a valve ball.
  • a holding piece 46 is arranged, in which a through hole 48 is present, in the longitudinal direction of the holding piece 46, that is in turn parallel to the longitudinal axis 29, runs.
  • 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 trained as a spiral spring Beaufschlagungselement 52 is pushed out of spring wire. A right in Figure 1 second end portion of the biasing member 52 of the
  • Pressure limiting valve 22 is in a cylindrical end of the
  • Pressure relief valve can be adjusted before use via the spring force of the valve spring 52 and the Einpressianae the valve body 38.
  • Pressure relief valve 22 shown as a ball valve.
  • a conical valve seat surface 56 is present.
  • Valve seat surface 56 is designed as a throttle bore formed first portion 60.
  • a likewise circular cylindrical second portion 62 is provided, which constitutes a guide for the valve element 44.
  • the wear can take place in particular within the wear width b, so that the diameter of the seal can vary within this range, so that the
  • Sealing diameter is either smaller than when new or larger than when new.
  • the difference between the minimum sealing ring radius r 2 which can be entered over the service life and the maximum direct ring radius r 3 represents the wear width b.
  • the ball can continue to wear in the direction of the opening direction 58 over time due to the wear by the amount X move opposite closing direction 68. This can result in particular in a reduction of the sealing diameter, which leads to a higher opening pressure, since the opening pressure is determined by the hydraulic force against the spring force, which is composed of the hydraulic pressure and the area on which the pressure acts, wherein this area just determined by the sealing diameter.
  • the wear width b is reduced by changing the geometry in the area of the valve seat surface 56.
  • a first conical first intermediate surface 70 which widens in the opening direction 58 and encloses an angle m with the central longitudinal axis 29, initially adjoins the throttle bore 60.
  • a first transition surface 72 which is tubular and thus circular cylindrical, and which forms an angle y of 0 ° with the central longitudinal axis 29, so that this surface consequently extends parallel to the central longitudinal axis 29.
  • Transition surface 72 then connects to the valve seat surface 56.
  • This step may have a length I of, for example, 2 mm and a depth t of, for example, 0.01 mm.
  • the contact point 64 and thus the sealing ring 66 may lie, in particular, at the transition 74 from the first transition surface 72 to the valve seat surface 56.
  • the minimum sealing ring radius r2 occurring due to wear can be increased in comparison to the configuration in FIG. 3, so that the opening pressure does not increase due to wear.
  • a second intermediate surface 70 is likewise present, in this case the angle m is 90 °, so that this surface forms a circular ring and extends orthogonally to the central longitudinal axis 29. At this second interface 70 in turn closes the second
  • the wear width b is further reduced by the following measure: A second transition surface 76 adjoins the valve seat surface 56 in the opening direction 58. This second Transition surface 76 includes an angle ⁇ of 90 ° with the central longitudinal axis 29. The second transition surface 76 finally opens into the second circular cylindrical surface 62.
  • the angle ⁇ according to FIG. 6 is 135 °, so that the
  • Wear width b in turn is reduced compared to the embodiment of Figure 5.
  • An optimal wear width reduction is obtained according to FIG. 7 in that the angle ⁇ is 180 °, so that the
  • Transition surface 76 extends from the transition 78 between the valve seat surface 56 in the closing direction 68.
  • the second transitional surface 76 in turn is followed by a second intermediate surface 80 extending orthogonally to the central longitudinal axis 29.
  • the radius r3 according to FIG. 7 at the transition 78 from the valve seat surface 56 to the second transition surface 76 determines the maximum sealing ring radius in the event of wear.
  • Opening pressure change can be achieved.

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

L'invention concerne une soupape de limitation de pression, comprenant un corps de soupape pourvu d'une surface de siège de soupape conique, qui forme un angle α avec un axe longitudinal médian du corps de soupape, et d'un élément de soupape et un élément de sollicitation, qui sollicite l'élément de soupape dans le sens opposé au sens d'ouverture à l'encontre de la surface de siège de soupape. Le corps de soupape présente dans le sens d'ouverture devant la surface de siège de soupape une première section tubulaire. L'invention prévoit entre ladite section et la surface de siège de soupape une première surface de transition jouxtant la surface de siège de soupape, qui forme avec un axe longitudinal médian du corps de soupape un angle γ, l'angle γ étant inférieur à l'angle α ; et/ou l'invention prévoit que le corps de soupape présente dans le sens d'ouverture après la surface de siège de soupape une deuxième section tubulaire. L'invention prévoit entre ladite section et la surface de siège de soupape une deuxième surface de transition jouxtant la surface de siège de soupape, qui forme avec un axe longitudinal médian du corps de soupape un angle β, l'angle β étant supérieur à l'angle α.
PCT/EP2019/050073 2018-02-27 2019-01-03 Soupape de limitation de pression WO2019166136A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018202928.8A DE102018202928A1 (de) 2018-02-27 2018-02-27 Druckbegrenzungsventil
DE102018202928.8 2018-02-27

Publications (1)

Publication Number Publication Date
WO2019166136A1 true WO2019166136A1 (fr) 2019-09-06

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Family Applications (1)

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PCT/EP2019/050073 WO2019166136A1 (fr) 2018-02-27 2019-01-03 Soupape de limitation de pression

Country Status (2)

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DE (1) DE102018202928A1 (fr)
WO (1) WO2019166136A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021013507A1 (fr) * 2019-07-19 2021-01-28 Robert Bosch Gmbh Pompe à carburant à haute pression

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0325211A1 (fr) * 1988-01-18 1989-07-26 Diesel Kiki Co., Ltd. Soupape d'équilibrage de pression
WO2002025148A1 (fr) * 2000-09-21 2002-03-28 Siemens Aktiengesellschaft Soupape de limitation de pression
EP2333304A1 (fr) * 2006-04-25 2011-06-15 Robert Bosch GmbH Pompe à carburant à haute pression
WO2016181755A1 (fr) * 2015-05-12 2016-11-17 日立オートモティブシステムズ株式会社 Pompe à carburant à haute pression
DE102016213333A1 (de) * 2016-07-21 2018-01-25 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0325211A1 (fr) * 1988-01-18 1989-07-26 Diesel Kiki Co., Ltd. Soupape d'équilibrage de pression
WO2002025148A1 (fr) * 2000-09-21 2002-03-28 Siemens Aktiengesellschaft Soupape de limitation de pression
EP2333304A1 (fr) * 2006-04-25 2011-06-15 Robert Bosch GmbH Pompe à carburant à haute pression
WO2016181755A1 (fr) * 2015-05-12 2016-11-17 日立オートモティブシステムズ株式会社 Pompe à carburant à haute pression
DE102016213333A1 (de) * 2016-07-21 2018-01-25 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021013507A1 (fr) * 2019-07-19 2021-01-28 Robert Bosch Gmbh Pompe à carburant à haute pression

Also Published As

Publication number Publication date
DE102018202928A1 (de) 2019-08-29

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