WO2013092972A1 - Soupape de limitation de pression - Google Patents

Soupape de limitation de pression Download PDF

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Publication number
WO2013092972A1
WO2013092972A1 PCT/EP2012/076588 EP2012076588W WO2013092972A1 WO 2013092972 A1 WO2013092972 A1 WO 2013092972A1 EP 2012076588 W EP2012076588 W EP 2012076588W WO 2013092972 A1 WO2013092972 A1 WO 2013092972A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
chamber
low
bore
Prior art date
Application number
PCT/EP2012/076588
Other languages
German (de)
English (en)
Inventor
Vittorio Caroli
Marek GOMOLA
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 WO2013092972A1 publication Critical patent/WO2013092972A1/fr

Links

Classifications

    • 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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0056—Throttling valves, e.g. having variable opening positions throttling the flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/22—Safety or indicating devices for abnormal conditions
    • F02D2041/227—Limping Home, i.e. taking specific engine control measures at abnormal conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/22—Safety or indicating devices for abnormal conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3863—Controlling the fuel pressure by controlling the flow out of the common rail, e.g. using pressure relief valves

Definitions

  • the invention relates to a pressure relief valve, in particular for common rail systems according to the preamble of claim 1.
  • Pressure relief valves for common rail systems are used for
  • Pressure limitation of the pressure in a high pressure accumulator of a common rail injection device The purpose of the pressure limiting valve is to limit the maximum rail pressure in the system in order to protect the system components in the event of a fault. Furthermore, the dirt control valve has the task for emergency travel of the motor vehicle, a minimum pressure in
  • a pressure relief valve which has a valve carrier and a valve carrier connected to the valve insert, wherein in the valve insert, a valve piston is slidably mounted.
  • the valve piston acts with a valve seat surface on a valve seat on the valve insert, wherein in the closed state of the pressure relief valve, the valve surface is seated on the valve seat.
  • the closing force of the valve piston is applied by a compression spring, which is accommodated in the valve carrier.
  • the pressure limiting valve is inserted in a housing which has a high-pressure connection to a high-pressure accumulator (common rail) and a low-pressure connection for a return line. In this case, the valve piston in the valve seat separates one
  • High-pressure valve chamber in which the high pressure port opens, from a low pressure chamber, which leads out of the low pressure port.
  • Object of the present invention is to provide a pressure relief valve in which the leakage pressure from the valve chamber can be safely and easily derived.
  • the relief hole is formed by a low-pressure side axial bore and a valve chamber side oblique bore, wherein the low-pressure side axial bore is a blind hole which is parallel to the axis of the valve piston and radially offset and opens at a low-pressure side end face of the valve piston in the low pressure chamber.
  • the oblique bore leads from the axial bore to an opening at a recess of the valve piston.
  • the course of the oblique bore leads at an angle from the opening at the recess to the axial bore, wherein the angle between the axis of the valve piston and the axis of
  • Diagonal bore is measured.
  • the angle is about 40 degrees.
  • the diameter of the axial bore is greater than the diameter of the oblique bore.
  • the formation of the low-pressure-side end face with a convex, convex surface shape has the advantage that the opening of the axial bore located there is not closed by the dial when the dial is resting on the low-pressure side end face, but that at least one lateral gap flows through the leakage between
  • valve piston To form a correspondingly dimensioned valve chamber, it is expedient for the valve piston to have three recesses distributed uniformly over the circumference.
  • Figure 1 is a sectional view of a built-in a housing
  • FIG. 2 shows an enlarged partial sectional view of a valve piston in FIG. 1
  • FIG. 3 shows an enlarged side view of the valve piston in FIG. 1
  • Figure 4 is an enlarged sectional view of the valve piston in
  • Figure 5 is an enlarged sectional view of the valve piston in
  • the pressure limiting valve in Figure 1 has a valve carrier 10 with a receiving space 11 for a closing spring 16 and a valve core 12 with a guide bore 13.
  • a valve piston 14 In the guide bore 13 is a valve piston 14 with a guide portion 41 out.
  • the valve piston 14 has a
  • Valve seat surface 19 and opposite a low-pressure side face 45 In the bottom of the guide bore 13, a valve seat 18 is formed around a throttle bore 15 around which the valve seat surface 19, which is formed on the valve piston 14, is seated when the pressure relief valve is closed.
  • Closing force for the valve piston 14 on the valve seat 18 is applied by the closing spring 16 designed as a compression spring.
  • the closing spring 16 is supported on the valve seat side on a shim 21, which rests on the low-pressure side face 45. On the opposite side, the closing spring 16 is supported on an inner end face of the receiving space
  • valve carrier 10 further surrounds with a paragraph 22 the
  • Valve insert 12 and is firmly connected to the valve core 12 at this point.
  • the pressure relief valve is inserted into a receptacle 23 of a housing 24.
  • a thread is carried out on the valve carrier 10, which in a
  • Low pressure port 26 has, which is connected to a not-shown low-pressure / return line.
  • a plane surface 28 is executed, on which the valve insert 12 is seated with an annular surface 29. Between ring surface 29,
  • a gap 30 is formed, in which a high-pressure hydraulic port 31 opens, which communicates with a high-pressure accumulator (common rail), not shown.
  • the gap 30 forms a valve seat 18 upstream high pressure chamber 33 am
  • the receiving space 11 is connected via a hydraulic connecting channel 35 with the annular chamber 27.
  • the annular chamber 27 via the low pressure port 26 to the low pressure / return line is thus also in Reception chamber 11, the low pressure of the low pressure / return line, so that the receiving space 11 forms a low-pressure chamber 36.
  • valve seat 18 i. upstream of the valve seat 18 is formed between the guide bore 13 and the valve piston 14, a valve chamber 40, the
  • High pressure chamber 33 is opened or closed via the valve seat 18, and the low pressure chamber 36 back from the guide portion 41 of
  • Valve piston 14 is limited in the guide bore 13.
  • the valve piston 14 furthermore has at least one recess 42 with a flat section 43 and an oblique section 44 running out on the guide section, preferably three recesses 42 distributed uniformly over the circumference. About the recess 42 of the rail pressure is regulated during emergency. The recesses 42 also increase the volume of the valve chamber 40.
  • the valve chamber 40 is opened or closed by means of the valve seat 18 to the high-pressure chamber 33.
  • the pressure in the high-pressure accumulator is maintained at its present level (FIG. 4). If the valve piston 14 lifts against the closing force of the closing spring 16 (FIG. 5), it releases the valve seat 18 and, at the same time, a gap between the guide bore 13 and the valve piston 14 is released via the recess 42, providing a hydraulic connection between the valve chamber 40 and the low-pressure chamber 36 manufactures.
  • the high pressure can be reduced from the high pressure chamber 33 via the throttle bore 15 and the valve chamber 40 in the low pressure chamber 36 and discharged from there into the Niederduck / return line.
  • Opening direction of the valve piston 14 against the closing spring 16 acts. As a result, the opening pressure set by the valve spring 16 or via the adjusting disk 21 for opening the pressure limiting valve is reduced.
  • a leakage connection is formed, which connects the valve chamber 40 with the low-pressure chamber 36 hydraulically,
  • the leakage connection is formed by at least one relief hole 50 which passes through the valve piston 14 and at one end into the valve chamber 40 and at one another end in the low-pressure chamber 36 opens.
  • the relief hole 50 is shown in FIG 2 of a
  • the low-pressure-side axial bore 51 is a blind hole which extends parallel to the axis of the valve piston 14 and, for example, radially offset therefrom and opens at the low-pressure-side end face 45 into the low-pressure space 36.
  • the oblique bore 52 leads from the
  • the oblique bore 52 leads with an acute angle a in the
  • Axial bore 51 wherein the angle a between the axis of the valve piston 14 and the axis of the oblique bore 52 is measured.
  • the angle a is for example about 40 degrees.
  • Valve seat 18 ( Figure 4).
  • the accumulating in the valve chamber 40 leakage from the high-pressure chamber 33 can consequently flow through the inclined bore 52 and the axial bore 51 in the low-pressure chamber 36.
  • no assist pressure exerted by the leakage builds up in the valve chamber 40, so that the opening force of the valve piston 14 is formed exclusively by the closing force of the closing spring 16.
  • valve piston 14 lifts off from the valve seat 18, the valve piston 14 reaches an axial position in which the opening 54 lies outside the guide bore 13 at the recess 42 and a throttle gap 55 is formed at the recess 42 between valve piston 14 and guide bore 13 , Fuel can flow out of the valve chamber 40 into the low-pressure chamber 36 via the throttle gap 55 in accordance with the indicated arrows in FIG. This position of the valve piston 14 represents the
  • Not marsraillac is generated by the action of the throttle gap 55.

Landscapes

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

Abstract

L'invention concerne une soupape de limitation de pression, en particulier pour un système de rampe commune. La soupape de limitation de pression comporte un support (10), une garniture (12) reliée au support (10), un piston (14) monté coulissant dans la garniture (12) ainsi qu'un ressort de fermeture (16) qui agit sur le piston (14) en exerçant une force de fermeture dans le sens de fermeture. Le piston (14) agit au moyen de la force de fermeture sur un siège (18) de soupape qui établit une liaison entre un espace haute pression (33) et un espace basse pression (36) par l'intermédiaire d'une chambre (40) de soupape dès que la force hydraulique agissant sur le piston (14) dans le sens d'ouverture dépasse la force de fermeture du ressort de fermeture (16). Une liaison de fuite qui permet, lorsque le siège (18) de soupape est fermé, une évacuation de la fuite de la chambre (40) de soupape dans l'espace basse pression (36), est formée entre la chambre (40) de soupape et l'espace basse pression (36). La liaison de fuite est formée par au moins un orifice de décharge (50) qui s'étend à travers le piston (14) et débouche, à une extrémité, dans la chambre (40) de soupape et, à une autre extrémité, dans l'espace à basse pression (36).
PCT/EP2012/076588 2011-12-23 2012-12-21 Soupape de limitation de pression WO2013092972A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110089844 DE102011089844A1 (de) 2011-12-23 2011-12-23 Druckbegrenzungsventil
DE102011089844.1 2011-12-23

Publications (1)

Publication Number Publication Date
WO2013092972A1 true WO2013092972A1 (fr) 2013-06-27

Family

ID=47553016

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/076588 WO2013092972A1 (fr) 2011-12-23 2012-12-21 Soupape de limitation de pression

Country Status (2)

Country Link
DE (1) DE102011089844A1 (fr)
WO (1) WO2013092972A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015205380A1 (de) 2015-03-25 2016-09-29 Robert Bosch Gmbh Druckbegrenzungsventil
DE102015205376A1 (de) 2015-03-25 2016-09-29 Robert Bosch Gmbh Druckbegrenzungsventil
CN109339965B (zh) * 2018-12-19 2021-07-23 重庆红江机械有限责任公司 一种用于共轨系统的压力控制阀

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4172470A (en) * 1978-06-02 1979-10-30 Mcdonnell Douglas Corporation Soft seat valve
FR2600141A1 (fr) * 1986-06-16 1987-12-18 Gay Alain Soupapes a compensations
FR2699640A1 (fr) * 1992-12-21 1994-06-24 Schrader Corps de clapet pour valve de retenue à grand débit.
US5533548A (en) * 1995-05-18 1996-07-09 Caterpillar Inc. Valving interface for a poppet valve
US5918628A (en) * 1997-06-17 1999-07-06 Parker-Hannifin Corporation Multi-stage check valve
FR2814201A1 (fr) * 2000-09-20 2002-03-22 Bosch Gmbh Robert Soupape de commande de liquides comportant une conduite d'evacuation centrale des fuites
WO2002053957A1 (fr) * 2000-12-29 2002-07-11 Chang-Hyeon Ji Soupape adaptee a la detection de fuite
US20030172973A1 (en) * 2002-03-12 2003-09-18 Surpass Industry Co., Ltd. Check valve
US20040107999A1 (en) * 2002-12-10 2004-06-10 Waffler Burdell Eugene Pressure relief valve assembly
WO2004083695A1 (fr) 2003-03-19 2004-09-30 Robert Bosch Gmbh Soupape de limitation de pression
US20100037615A1 (en) * 2008-08-18 2010-02-18 Delavan Inc. Multi-stage check valve
EP2282089A1 (fr) * 2009-08-05 2011-02-09 HAWE Hydraulik SE Soupape hydraulique
DE102011017765A1 (de) 2011-04-29 2012-10-31 Robert Bosch Gmbh Druckbegrenzungsventil

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4172470A (en) * 1978-06-02 1979-10-30 Mcdonnell Douglas Corporation Soft seat valve
FR2600141A1 (fr) * 1986-06-16 1987-12-18 Gay Alain Soupapes a compensations
FR2699640A1 (fr) * 1992-12-21 1994-06-24 Schrader Corps de clapet pour valve de retenue à grand débit.
US5533548A (en) * 1995-05-18 1996-07-09 Caterpillar Inc. Valving interface for a poppet valve
US5918628A (en) * 1997-06-17 1999-07-06 Parker-Hannifin Corporation Multi-stage check valve
FR2814201A1 (fr) * 2000-09-20 2002-03-22 Bosch Gmbh Robert Soupape de commande de liquides comportant une conduite d'evacuation centrale des fuites
WO2002053957A1 (fr) * 2000-12-29 2002-07-11 Chang-Hyeon Ji Soupape adaptee a la detection de fuite
US20030172973A1 (en) * 2002-03-12 2003-09-18 Surpass Industry Co., Ltd. Check valve
US20040107999A1 (en) * 2002-12-10 2004-06-10 Waffler Burdell Eugene Pressure relief valve assembly
WO2004083695A1 (fr) 2003-03-19 2004-09-30 Robert Bosch Gmbh Soupape de limitation de pression
US20100037615A1 (en) * 2008-08-18 2010-02-18 Delavan Inc. Multi-stage check valve
EP2282089A1 (fr) * 2009-08-05 2011-02-09 HAWE Hydraulik SE Soupape hydraulique
DE102011017765A1 (de) 2011-04-29 2012-10-31 Robert Bosch Gmbh Druckbegrenzungsventil

Also Published As

Publication number Publication date
DE102011089844A1 (de) 2013-06-27

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