WO2013079693A1 - Système de soupape - Google Patents

Système de soupape Download PDF

Info

Publication number
WO2013079693A1
WO2013079693A1 PCT/EP2012/074152 EP2012074152W WO2013079693A1 WO 2013079693 A1 WO2013079693 A1 WO 2013079693A1 EP 2012074152 W EP2012074152 W EP 2012074152W WO 2013079693 A1 WO2013079693 A1 WO 2013079693A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
flow control
scroll spring
control valve
fluid
Prior art date
Application number
PCT/EP2012/074152
Other languages
German (de)
English (en)
Inventor
Matthias Bleeck
Bernd Gugel
Burhan Dagdelen
Original Assignee
Continental Automotive 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 Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Publication of WO2013079693A1 publication Critical patent/WO2013079693A1/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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M59/367—Pump inlet valves of the check valve type being open when actuated
    • 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
    • F02M59/462—Delivery 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
    • F02M59/44—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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M63/0049—Combined valve units, e.g. for controlling pumping chamber and injection valve
    • 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
    • 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
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • 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
    • F16K15/14—Check valves with flexible valve members
    • F16K15/141—Check valves with flexible valve members the closure elements not being fixed to the valve body
    • F16K15/142—Check valves with flexible valve members the closure elements not being fixed to the valve body the closure elements being shaped as solids of revolution, e.g. toroidal or cylindrical rings
    • 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
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0644—One-way valve
    • F16K31/0655—Lift valves
    • F16K31/0665—Lift valves with valve member being at least partially ball-shaped

Definitions

  • Valve arrangement The invention relates to a valve arrangement, in particular a valve arrangement for a high-pressure pump for an internal combustion engine.
  • injection systems For injecting fuel into combustion chambers of an internal combustion engine, in particular a diesel internal combustion engine or gasoline internal combustion engine, injection systems are used, which are designed as so-called common rail systems.
  • injectors from a common fuel storage, the common rail, supplied with fuel.
  • the fuel to be injected is in the
  • Injection systems for internal combustion engines usually have different pumps, by means of which fuel is conveyed to be introduced into combustion chambers of the internal combustion engine.
  • Such injection systems for internal combustion engines place high demands on the accuracy of the injection pressure required for injecting the fuel into the combustion chambers of the internal combustion engine.
  • the pumps which provide the necessary volume flow and the required fluid pressure, are subject to heavy loads, in particular mechanical stresses, in accumulator injection systems. From the individual components of such high-pressure pumps, such as the valves, large forces must be absorbed.
  • a valve arrangement comprises a volume flow control valve, which is designed to adjust a fluid inflow into a pump.
  • the valve assembly includes a check valve coupled to the flow control valve downstream of the flow control valve.
  • the check valve is designed as a scroll spring.
  • the flow control valve is protected from pressure peaks from the downstream area.
  • the valve arrangement is in particular part of a high-pressure injection system of a motor vehicle. Pressure peaks from the high-pressure region, which is arranged downstream of the volume flow control valve, are damped by the check valve or is prevented by the check valve that the pressure peaks reach into inner regions of the volume flow control valve.
  • the scroll spring is designed so that it expands at a volume flow from the flow control valve and releases the fluid flow through the flow control valve in the direction of the high pressure region. A fluid flow in the opposite direction from the high-pressure region into the inner regions of the volume flow control valve is prevented by the scroll spring, since this is compressed by such a fluid flow St compressed. In the compressed state, the scroll spring is fluid-tight.
  • the volume flow control valve has a housing with a longitudinal axis surrounding a fluid inlet and a fluid outlet.
  • the scroll spring surrounds the housing coaxially with the longitudinal axis.
  • the scroll spring is in particular arranged so that it has a contact surface with the housing.
  • the scroll spring and the housing according to Embodiments on a direct contact with each other.
  • the scroll spring is wrapped around the housing.
  • the scroll spring has a first and a second end region, wherein the first end region is arranged so that the first end region overlaps the second end region.
  • the scroll spring has a central region which is arranged between the first and the second end region and which is formed in one layer.
  • the central region has a greater proportion of the roll spring than the overlapping end regions.
  • the scroll spring is formed from a spiral-shaped sheet metal.
  • the overlapping end portions are pressed against each other in the sealing state of the check valve. This prevents fluid flow through the check valve since the fluid can not get between the two overlapping end portions.
  • a fluid flow in the direction of the high-pressure region is released by the check valve, since the fluid flows outwardly from the inner of the scroll spring and thereby lifts the first end region from the second end region, so that there is a gap between the first end region and the second end region. Through this gap, the fluid flows.
  • the scroll spring is formed so that only overlap the two end portions and the majority of the scroll spring is formed without overlap.
  • FIG. 1 shows a schematic representation of a valve arrangement according to an embodiment
  • Figure 2 is a schematic representation of a check valve according to an embodiment in a first state
  • Figure 3 is a schematic representation of the check valve in another state.
  • FIG. 1 shows a schematic cross-sectional view of a valve arrangement 100.
  • the valve arrangement 100 has a volume flow control valve 110.
  • the valve assembly 100 further includes a check valve 120.
  • the volumetric flow control valve 110 is configured to adjust a fluid flow into a high-pressure pump, which is arranged downstream of the volumetric flow control valve 110.
  • the volume flow control valve 110 has a housing 111 with a longitudinal axis L.
  • the housing 111 surrounds a fluid inlet 112 and a fluid outlet 113.
  • a valve tappet 114 is disposed between the fluid inlet 112 and the fluid outlet 113.
  • the valve tappet 114 cooperates with a valve seat 115.
  • a fluid flow from the fluid inlet 112 to the fluid outlet 113 is made possible.
  • the valve lifter 114 abuts the sealing seat 115, fluid flow from the fluid inlet 112 to the fluid outlet 113 is inhibited.
  • the valve tappet 114 is movable by an actuator 117.
  • the actuator 117 is, for example, a magnetic actuator or a piezoelectric actuator.
  • a spring 116 which is disposed between the housing 111 and the valve stem 114, exerts a spring force on the valve stem 114, which is directed against an actuator force of the actuator 117.
  • the spring 116 is configured to press the valve lifter 114 against the sealing seat 115.
  • the volumetric flow control valve 110 controls the hydraulic volumetric flow through the volumetric flow control valve
  • the check valve 120 is formed as a scroll spring.
  • Rolling spring ( Figure 2) is formed in plan view circular or spiral.
  • the scroll spring is formed from a sheet metal strip which is rolled up so that a first end portion 122 overlaps a second end portion 123.
  • a central portion 124 between the two end portions 122 and 123 is formed in a single layer and has no portion of the scroll spring that overlaps it.
  • the scroll spring is arranged on the housing 111 in the region of the fluid outlet 113.
  • the scroll spring has a common contact surface 121 with the housing 111.
  • the housing 111 and the scroll spring touch each other.
  • the contact surface 121 surrounds the housing 111 in a circle.
  • the scroll spring is arranged coaxially with the longitudinal axis L on the housing 111.
  • the scroll spring is in particular connected to the housing 111 such that the contact surface 111 is fluid-tight. For the fluid, it is only possible the housing
  • the gap 125 is formed between the two End portions 122 and 123, when the first end portion 122 is spaced from the second end portion 123.
  • the check valve 120 blocks fluid flow from outside into the fluid outlet 113 when the first end portion 122 is in contact with the second end portion 123 (FIG. 3).
  • the fluid pushes the first end portion 122 on the second end portion 123 and thus no flow of the scroll spring between the two end portions 122 and 123 from the high-pressure region A in the direction of the low-pressure region P is possible.
  • the check valve 120 releases fluid flow from the fluid inlet 112 to the fluid outlet 113 and on to the downstream pump when the pressure on the flow control valve 110 side of the check valve 120 is greater than the pressure on the flow control valve 110 side away of the check valve 120.
  • the first end portion 122 is depressed from the second end portion 123 by the fluid flowing out of the fluid outlet 113 ( Figure 2).
  • the fluid flows through the resulting gap 125 between the first end portion 122 and the second end portion 123.
  • the fluid flows from a low pressure region P through the volume flow control valve 110 and the check valve 120 to a high pressure region A.
  • the check valve 120 When pressure peaks from the high pressure area A of the injection system, the check valve 120 is compressed, so that the fluid pressure acting on the check valve 120 from the outside, is greater than the fluid pressure in the fluid outlet 113 ( Figure 3).
  • the end portion 122 is pressed toward the end portion 123 and comes into contact with the end portion 123.
  • the two end portions 122 and 123 are compressed and thus seal the check valve 120, so that the pressure peaks can not enter the inside of the flow control valve 110.
  • the valve arrangement 100 with the volume flow control valve 110 and the check valve 120 which is designed as a scroll spring, the control behavior of the volume flow control valve 110 is improved because the pressure peaks from the high pressure region of the pump do not enter the interior of the volume flow control valve 110 or into the interior of the housing 111.
  • a force on the valve stem 114 by the pressure peaks, which has a movement of the valve stem 114 result is avoided. This allows precise and reliable control.
  • the volume flow control valve 110 is protected in a simple and cost-effective manner. Since the pressure peaks do not reach the interior of the volume flow control valve 110, the components of the volume flow control valve 110 are protected, in particular the magnetic components of the actuator 117. The pressure peaks, which conventionally lead to a rapid and uncontrolled movement, for example, the valve stem 114 are damped or completely blocked and Thus, the components of the flow control valve 110 protected against bursting. In particular, the magnet of the actuator 117 is protected because the pressure peaks do not act inside the magnet. Thus, reliable operation is possible.
  • the volume flow control valve 110 is formed in the illustrated embodiments as a seat valve.
  • the volume ⁇ flow control valve 110 is formed according to other embodiments in a different construction, for example, executed in a sliding construction, which has a pressure compensation ⁇ .
  • the check valve 120 is used in such Ausure ⁇ insurance forms primarily to protect the magnetic components of the flow control valve.

Abstract

L'invention concerne un système de soupape comprenant une soupape de commande de débit volumétrique (110) qui est conçue pour régler un afflux de fluide dans une pompe et un clapet antiretour (120) qui est accouplé à la soupape de commande de débit volumétrique (110) en aval de cette dernière (110) et qui est conçu comme ressort à col de cygne.
PCT/EP2012/074152 2011-12-02 2012-11-30 Système de soupape WO2013079693A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011087664.2 2011-12-02
DE201110087664 DE102011087664B4 (de) 2011-12-02 2011-12-02 Ventilanordnung

Publications (1)

Publication Number Publication Date
WO2013079693A1 true WO2013079693A1 (fr) 2013-06-06

Family

ID=47471705

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/074152 WO2013079693A1 (fr) 2011-12-02 2012-11-30 Système de soupape

Country Status (2)

Country Link
DE (1) DE102011087664B4 (fr)
WO (1) WO2013079693A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220768A1 (de) 2013-10-15 2015-04-16 Continental Automotive Gmbh Ventilanordnung
WO2018135584A1 (fr) * 2017-01-19 2018-07-26 株式会社デンソー Dispositif d'ajustage du réglage de distribution et clapet de non-retour

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015218343A1 (de) * 2015-09-24 2017-03-30 Robert Bosch Gmbh Hochdruckpumpe mit integriertem Saugventil

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0834655A1 (fr) * 1996-10-07 1998-04-08 Zexel Corporation Construction de soupape de décharge
DE102008043237A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
EP2386731A1 (fr) * 2010-05-03 2011-11-16 Hydraulik-Ring GmbH Soupape hydraulique

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10143433B4 (de) * 2001-09-05 2013-09-26 Hilite Germany Gmbh Proportionalventil
DE102005013085B3 (de) * 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
GB0616966D0 (en) * 2006-08-29 2006-10-04 Delphi Tech Inc Oil control valve
GB0618648D0 (en) * 2006-09-22 2006-11-01 Delphi Tech Inc Oil control valve
DE102010018200A1 (de) * 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Steuerventil, insbesondere Proportionalventil

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0834655A1 (fr) * 1996-10-07 1998-04-08 Zexel Corporation Construction de soupape de décharge
DE102008043237A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
EP2386731A1 (fr) * 2010-05-03 2011-11-16 Hydraulik-Ring GmbH Soupape hydraulique

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013220768A1 (de) 2013-10-15 2015-04-16 Continental Automotive Gmbh Ventilanordnung
JP2016508579A (ja) * 2013-10-15 2016-03-22 コンチネンタル オートモーティヴ ゲゼルシャフト ミット ベシュレンクテル ハフツングＣｏｎｔｉｎｅｎｔａｌ Ａｕｔｏｍｏｔｉｖｅ ＧｍｂＨ 弁アッセンブリ
US9719472B2 (en) 2013-10-15 2017-08-01 Continental Automotive Gmbh Valve arrangement
WO2018135584A1 (fr) * 2017-01-19 2018-07-26 株式会社デンソー Dispositif d'ajustage du réglage de distribution et clapet de non-retour

Also Published As

Publication number Publication date
DE102011087664B4 (de) 2014-03-20
DE102011087664A1 (de) 2013-06-06

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