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WO2010057701A2 - Vanne à bille pour pompes à haute pression - Google Patents

Vanne à bille pour pompes à haute pression Download PDF

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Publication number
WO2010057701A2
WO2010057701A2 PCT/EP2009/062270 EP2009062270W WO2010057701A2 WO 2010057701 A2 WO2010057701 A2 WO 2010057701A2 EP 2009062270 W EP2009062270 W EP 2009062270W WO 2010057701 A2 WO2010057701 A2 WO 2010057701A2
Authority
WO
WIPO (PCT)
Prior art keywords
valve
ball
sealing seat
valve according
seat
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/EP2009/062270
Other languages
German (de)
English (en)
Other versions
WO2010057701A3 (fr
Inventor
Wolfgang Stoecklein
Tobias Reiser
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 WO2010057701A2 publication Critical patent/WO2010057701A2/fr
Publication of WO2010057701A3 publication Critical patent/WO2010057701A3/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
    • 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
    • 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
    • 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
    • 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
    • F16K17/0433—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 vibration preventing means
    • 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
    • F16K25/00—Details relating to contact between valve members and seats

Definitions

  • the invention relates to a ball valve, in particular a high-pressure valve for high-pressure pumps of fuel injection systems of air-compressing, self-igniting internal combustion engines, and a high-pressure pump with such a ball valve.
  • a high-pressure pump for fuel injectors of internal combustion engines has a pump housing, in which a plurality of pump elements are arranged.
  • the pump elements convey liquid under high pressure via a high-pressure channel system to a common high-pressure connection.
  • an outlet valve is provided for each pump element, which opens to a memory.
  • Such an outlet valve has a valve ball acted upon by a valve spring, which interacts with a valve seat surface to form a sealing seat.
  • the ball valve according to the invention with the features of claim 1 and the high-pressure pump according to the invention with the features of claim 17 have the advantage that a reliable closing of the ball valve is ensured. Specifically, the operation of the high-pressure pump can be improved, in particular, the high-pressure pump can be operated at a higher speed or a higher volume flow.
  • the hydraulic properties of the ball valve can be improved. It can be prevented that the ball valve does not close at high speeds. Furthermore, the efficiency of a high-pressure pump can be increased with such a ball valve by a targeted improvement in the valve function.
  • oscillations and rotations can be excited about an axis of symmetry due to a high volume flow during the delivery phase. These oscillations have their origin in hydraulic flow forces.
  • the ball valve can quickly close, the oscillations and the rotation must be reduced by mechanical or hydraulic damping. Specifically, the ball valve closes only when a rotation of the valve ball at the transition from the delivery phase into the suction phase is small enough.
  • the hydraulic mechanisms that lead to Oszillationsanregung that is, the rotational and radial oscillations, the valve ball
  • the oscillation frequency of the valve ball can be reduced.
  • the closing time of the ball valve which affects the efficiency and the durability of the high-pressure pump can be reduced.
  • the high-pressure pump can be operated at a higher speed and thus a higher volume flow.
  • a tear-off edge and / or a chamfer is configured on the valve seat surface. It is also advantageous that the tear-off edge or the chamfer is formed relative to a diameter of the valve ball relatively close to the sealing seat.
  • the trailing edge or chamfer may have a distance from the sealing seat that is within a range of about 5% to about 15% of the diameter of the valve ball. This will prevent the flow from being applied to the valve ball, causing the pressure field on the valve ball acts, is reduced.
  • the tear-off edge or the chamfer can be arranged in the flow direction from the inlet to the outlet in front of or behind the sealing seat. In this case, demolition edges and / or chamfers can also be arranged both in front of and behind the sealing seat. A combination of trailing edge and chamfer is also possible here.
  • a ball guide for the valve ball which ensures a relatively close guidance of the ball on an axis during the opening and closing of the sealing seat. It is further advantageous that the ball guide predetermines a guide of the ball with a maximum radial displacement to the axis, which is from a range of about 5% to about 10% of a diameter of the valve ball.
  • a narrow ball guide the radial degree of freedom of the valve ball is limited.
  • the asymmetric distribution of the pressure on the ball surface of the valve ball is smaller and the rotational excitation remains smaller.
  • an opening or closing force always acts on the valve ball over the entire valve lift range, which has a positive effect on the valve stability.
  • the ball guide is configured by a bore which forms a valve space, wherein the valve ball is arranged in the valve chamber. Furthermore, it is advantageous that a valve spring is provided which acts on the valve ball in a closing direction for closing the sealing seat between the valve ball and the valve seat surface.
  • a stop element provided is that limits a stroke of the valve ball.
  • the stop element has a recess which forms a ball guide.
  • the recess has a centering surface, which tapers in an opening direction of the valve ball, in which the sealing seat is opened. In this way, a centering of the valve ball can be achieved when opening, so that a radial displacement is limited.
  • the centering surface is configured conically in an advantageous manner, wherein the centering surface is aligned with respect to an axis on which a center of the valve ball is located when the sealing seat is closed. As a result, a symmetrical pressure distribution is achieved on the spherical surface.
  • a valve spring which normally acts on the valve ball in a closing direction, omitted.
  • FIG. 1 shows a ball valve, which is integrated in a high pressure pump, in a schematic sectional view according to a first embodiment of the invention.
  • FIG. 2 shows the ball valve shown in FIG. 1 in accordance with a second embodiment of the invention
  • Fig. 3 corresponding to the ball valve shown in Fig. 1 a third embodiment of the invention.
  • FIG. 4 the ball valve shown in Fig. 1 according to a fourth embodiment of the invention.
  • Fig. 1 shows a ball valve 1, which is integrated in a housing part 2 of a high pressure pump, in a schematic sectional view according to a first embodiment of the invention.
  • the ball valve 1 is designed in particular as a high-pressure valve for high-pressure pumps of fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • the high-pressure pump whose housing part 2 is shown in Fig. 1 in part, be designed in particular as a radial or in-line piston pump to promote fuel to a common rail of the fuel injection system.
  • the ball valve 1 according to the invention and the high pressure pump according to the invention with such a ball valve 1 are also suitable for other applications.
  • the ball valve 1 has a valve ball 3, which is arranged in a valve chamber 4.
  • fuel flows in a flow direction 5 via an inlet 6 of the ball valve 1 into the valve chamber 4.
  • fuel flows out of the valve chamber 4 in a flow direction 5 'via a drain 7 of the ball valve 1.
  • the ball valve 1 has a valve seat surface 8, which is formed in this embodiment on the housing part 2.
  • valve ball 3 cooperates in the closed state of the ball valve 1 with the valve seat surface 8 to a closed sealing seat.
  • the valve ball 3 at least partially lifts off from the valve seat surface 8, as a result of which fuel in the flow direction 5 can flow into the valve chamber 4 via the inlet 6.
  • the sealing seat is predetermined by an at least substantially linear seat 9 on the valve seat surface 8.
  • the ball valve 1 has an axis 15. In the closed state, the valve ball 3 is centered on the axis 15. In Fig. 1, a situation is shown in which the valve ball 3 is slightly shifted with an open sealing seat in a radial direction 16 from an axial position. This results in slightly different flows on the valve ball 3. Thus, an asymmetrical pressure field with respect to the axis 15 results on the valve ball 3.
  • a tear-off edge 17 is provided in the flow direction 5 behind the sealing seat 9.
  • a seat length after the sealing seat 9 to the trailing edge 17 between 5% and 15% of a diameter 18 of the valve ball 3.
  • the flow can not or only slightly abut the valve ball 3, so that the pressure field and thus the asymmetric Design of the pressure field on the valve ball 3 is reduced.
  • a tear-off edge corresponding to the tear-off edge 17 can, viewed in the flow direction 5, also be arranged in front of the sealing seat 9.
  • a chamfer 19 is provided in front of the sealing seat 9, which also shortens the seat length in front of the sealing seat 9. Accordingly, instead of the tear-off edge 17, a chamfer may also be provided after the sealing seat 9.
  • the ball valve 1 also has a stop element 20 arranged in the valve space 4.
  • a maximum deflection of the valve ball 3 is limited by the stop element 20.
  • the stop element 20 receives in sections a valve spring 21, which acts on the valve ball 3 in a closing direction, that is opposite to the flow direction 5.
  • Fig. 2 shows the ball valve 1 shown in Fig. 1 according to a second embodiment of the invention.
  • the inlet 6 is designed as a stepped bore, wherein one of the
  • Valve seat surface 8 adjacent step 22 is provided. Through the step 22, a tear-off edge 17 'is provided in front of the sealing seat 9. Thus, the seat length is reduced in front of the sealing seat 9. This will also ensure that the flow can not or only to a lesser extent abut the valve ball 3, whereby the pressure field on the valve ball 3 decreases.
  • Fig. 3 shows the ball valve 1 shown in Fig. 1 according to a third embodiment.
  • a ball guide for the valve ball 3 in the valve chamber 4 is configured by a bore 23.
  • the valve ball is arranged in the valve space 4 formed by the bore 23.
  • the bore 23 is designed relatively narrow.
  • a radial displaceability of the valve ball 3 in a radial direction 16 is limited.
  • the limitation of the radial displaceability can be, for example, between about 5% and about 10% of the diameter 18 of the valve ball 3.
  • the valve ball 3 can be displaced by at most about 5% to about 10% from its axial starting position on the axis 15.
  • an asymmetrical configuration of the pressure field on the valve ball 3 that is, an asymmetrical distribution of the pressure on the surface of the valve ball 3, limited. This reduces a rotation or oscillation excitation.
  • an opening and closing force always acts on the valve ball 3 over the entire valve lift range, which has a positive effect on the valve stability.
  • Fig. 4 shows the ball valve 1 shown in Fig. 1 according to a fourth embodiment.
  • the stopper member 20 is disposed relatively close to the initial position of the valve ball 3, in which the ball valve 1 is closed.
  • the stop element 20 offers a massive stroke stop for the valve ball 3.
  • a stroke of the valve ball 3 is limited.
  • the stop element 20 has a recess 25 which faces the valve ball 3.
  • the valve ball 3 is located partially within the recess 25.
  • a centering surface 26 is formed, which is configured conical.
  • the centering surface 26 has a centering or opening angle 27, which is about 45 °.
  • the centering surface 26 tapers in a direction of flow 5 corresponding opening direction of the valve ball 3, in which the sealing seat 9 is opened.
  • the centering surface 26 is aligned with respect to the axis 15, on which a center point of the valve ball 3 is located when the sealing seat 9 is closed.
  • valve spring 21 as provided for example in the first embodiment described with reference to FIG. 1, omitted.
  • the ball valve 1 may be configured without such a valve spring.
  • the stop element 20 through the recess 25th the stop element 20 at least one radial
  • Embodiment predetermined centering or opening angle 27 of the centering surface 26 is preferably at least approximately equal to a valve seat angle 28, which is predetermined for the valve seat surface 8.

Landscapes

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

Abstract

L'invention concerne une vanne à bille (1), servant en particulier de vanne à haute pression pour les pompes à haute pression d'installations d'injection de carburant de machines à combustion interne à auto-allumage et à air comprimé. Cette vanne à bille comprend une bille de vanne (3) et une surface de siège de vanne (8). A cette occasion, la bille de vanne (3), afin d'interrompre la liaison entre une admission (6) et un refoulement (7), coopère avec la surface de siège de vanne (8) pour former un siège étanche. Par ailleurs, une excitation oscillatoire et/ou une excitation en rotation de la bille de vanne (3), agissant contre la fermeture du siège étanche (9) entre la bille de vanne (3) et la surface de siège de vanne (8), sont amorties. De ce fait, on obtient une fermeture fiable de la vanne à bille (1) pendant une course d'aspiration suivant une course de refoulement.
PCT/EP2009/062270 2008-11-19 2009-09-22 Vanne à bille pour pompes à haute pression Ceased WO2010057701A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008043841.3 2008-11-19
DE200810043841 DE102008043841A1 (de) 2008-11-19 2008-11-19 Kugelventil für Hochdruckpumpen

Publications (2)

Publication Number Publication Date
WO2010057701A2 true WO2010057701A2 (fr) 2010-05-27
WO2010057701A3 WO2010057701A3 (fr) 2010-07-29

Family

ID=41491481

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2009/062270 Ceased WO2010057701A2 (fr) 2008-11-19 2009-09-22 Vanne à bille pour pompes à haute pression

Country Status (2)

Country Link
DE (1) DE102008043841A1 (fr)
WO (1) WO2010057701A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103225703A (zh) * 2012-01-31 2013-07-31 株式会社电装 单向阀
CN105003371A (zh) * 2014-04-15 2015-10-28 罗伯特·博世有限公司 燃料高压泵，具有包括阀体和阀球的出口阀
CN113661104A (zh) * 2019-04-03 2021-11-16 罗伯特·博世有限公司 阀组件

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010039516A1 (de) 2010-08-19 2012-02-23 Robert Bosch Gmbh Ventil, insbesondere einer hydraulischen Kolbenpumpe
DE102010040284A1 (de) 2010-09-06 2012-03-08 Robert Bosch Gmbh Ventil, insbesondere einer hydraulischen Kolbenpumpe
DE102010040617A1 (de) 2010-09-13 2012-03-15 Robert Bosch Gmbh Ventil, insbesondere einer hydraulischen Kolbenpumpe
DE102010062173A1 (de) 2010-11-30 2012-05-31 Robert Bosch Gmbh Ventil, insbesondere Auslassventil einer hydraulischen Kolbenpumpe
DE102010062174A1 (de) 2010-11-30 2012-05-31 Robert Bosch Gmbh Ventil, insbesondere ein Auslassventil einer hydraulischen Kolbenpumpe
DE102010063357A1 (de) 2010-12-17 2012-06-21 Robert Bosch Gmbh Ventil für eine hydraulische Kolbenpumpe
DE102012209226A1 (de) * 2012-05-31 2013-12-05 Robert Bosch Gmbh Druckregelventil
JP6432440B2 (ja) * 2015-05-15 2018-12-05 株式会社デンソー 高圧ポンプ

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5037277A (en) * 1989-07-26 1991-08-06 Flow International Corporation Poppet valve for a high pressure fluid pump
JP3925376B2 (ja) * 2002-09-30 2007-06-06 株式会社デンソー 高圧燃料ポンプ
DE10247142A1 (de) 2002-10-09 2004-04-22 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE10355030A1 (de) * 2003-11-25 2005-06-23 Robert Bosch Gmbh Ventil, insbesondere für eine Hochdruckpumpe einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine
JP2006242019A (ja) * 2005-03-01 2006-09-14 Jtekt Corp 燃料ポンプ用チェック弁

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103225703A (zh) * 2012-01-31 2013-07-31 株式会社电装 单向阀
CN105003371A (zh) * 2014-04-15 2015-10-28 罗伯特·博世有限公司 燃料高压泵，具有包括阀体和阀球的出口阀
CN105003371B (zh) * 2014-04-15 2019-06-28 罗伯特·博世有限公司 燃料高压泵，具有包括阀体和阀球的出口阀
CN113661104A (zh) * 2019-04-03 2021-11-16 罗伯特·博世有限公司 阀组件

Also Published As

Publication number Publication date
WO2010057701A3 (fr) 2010-07-29
DE102008043841A1 (de) 2010-05-20

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