EP1252429B1 - Ventil zum steuern von flüssigkeiten - Google Patents

Ventil zum steuern von flüssigkeiten Download PDF

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Publication number
EP1252429B1
EP1252429B1 EP01909462A EP01909462A EP1252429B1 EP 1252429 B1 EP1252429 B1 EP 1252429B1 EP 01909462 A EP01909462 A EP 01909462A EP 01909462 A EP01909462 A EP 01909462A EP 1252429 B1 EP1252429 B1 EP 1252429B1
Authority
EP
European Patent Office
Prior art keywords
valve
piston
seat
passage
pressure chamber
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.)
Expired - Lifetime
Application number
EP01909462A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1252429A2 (de
Inventor
Friedrich Boecking
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 EP1252429A2 publication Critical patent/EP1252429A2/de
Application granted granted Critical
Publication of EP1252429B1 publication Critical patent/EP1252429B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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
    • 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
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/50—Arrangements of springs for valves used in fuel injectors or fuel injection pumps
    • F02M2200/502—Springs biasing the valve member to the open position

Definitions

  • the invention relates to a valve for controlling fluids according to the preamble of claim 1.
  • a valve is known in which in a stepped bore of the valve housing, an actuating piston of a valve member is slidably disposed in a portion of the stepped bore with a small diameter.
  • a movable by a piezoelectric actuator larger piston is arranged in a portion of the stepped bore with a larger diameter.
  • a filled with a pressure medium hydraulic pressure chamber is formed so that a hydraulic translation of a movement of the piezoelectric actuator takes place.
  • the actuating piston of the valve member makes a stroke increased by the gear ratio of the piston diameter, since the piston of the piezoelectric actuator has a larger area than the actuating piston of the valve member.
  • 3/2-control valves are used, as disclosed for example in US 5,738,075.
  • Such 3/2 control valves can be designed as a seat slide or seat-seat valves.
  • the pressure from a rail by means of a controllable piston via a pressure chamber and a booster piston to a control chamber, from which the fuel is injected into the combustion chamber, out.
  • the pressure chamber is connected to a leak oil line, so that there is leak oil pressure in the pressure chamber.
  • a connection between the high pressure area and the leak oil area occurs for a short time. This results in a so-called Ab Kunststoffmaschinen in the drain line.
  • the discharge of the control chamber of the valve is hindered until the valve has sealed the opening to the high pressure area.
  • a valve according to the preamble of claim 1 is known from DE-A-19 716 221.
  • the valve according to the invention for controlling fluids with the characterizing features of claim 1 has the advantage that such a Ab horrstoss to the leak oil line does not occur. This is prevented by an upstream of a slide element on the seat of the control valve.
  • the slide element is arranged in the opening direction immediately before the region of the piston, with which the piston is seated on the valve seat. This allows, depending on the stroke of the slide element, a delayed opening of the passage between the inlet line and the pressure chamber, but an immediate closing of the passage between the inlet line and the pressure chamber. Thus, it can be ensured at any time when switching the control valve that there is no connection between the inlet pipe and the drain line.
  • the stroke of the piston for opening the connection between the supply line and the pressure chamber is at least equal to, but advantageously larger than a stroke for closing or opening a passage between the pressure chamber of the.
  • the slide element of the piston is cylindrical. In this way, on the one hand, a simple production of the slide element can be achieved, on the other hand, a simple construction of the control valve is thereby made possible overall.
  • the piston of the control valve is designed in two parts.
  • a seat slide valve can be realized with an interposed pressure chamber.
  • the control valve is constructed as a force-equalizing valve.
  • the guide diameter on the valve seat corresponds to the diameter of the slide element.
  • the piston of the control valve is integrally formed. This allows a 3/2-seat gate valve to be used as an exhaust valve.
  • valve will be designed to control fluids as a 3/2-seat gate valve or a 3/2-seat seat valve.
  • an optimum slide ratio can be formed from the respective stroke lengths.
  • the coverage should be chosen so that no appreciable delays of the valve occur, but it is ensured that no Abgresific occurs in the drain line.
  • valve according to the invention is used in a pressure-translated common rail injector.
  • the valve according to the invention is designed here as a 3/2-seat slide control valve 1.
  • a fuel injection valve according to a first embodiment of the present invention is shown.
  • the fuel injection valve the 3/2-control valve 1.
  • the control valve 1 consists of an actuating element 2 and a first piston 3 and a second piston 4.
  • an actuating element 2 for example, a known magnetic actuator or a known piezo actuator can be used.
  • the first piston 3 consists of several piston sections 3a to 3e.
  • a first piston portion 3a is cylindrical and communicates with the actuator 2 in connection.
  • a second piston section 3b which is of concave design and, with a corresponding position of the piston 3, releases a first passage 10 on the valve seat.
  • the third piston section designed as a slide element 3c follows.
  • the third piston section 3 c is arranged directly on the valve seat or on the first passage 10.
  • the piston 2 still comprises a widening fourth piston section 3d and a further cylindrical fifth piston section 3e.
  • the fifth piston section 3e communicates with a pressure chamber 6 arranged between the first piston 3 and the second piston 4.
  • the second piston 4 consists of a slide element 4a and a base body 4b.
  • the piston 4 is held by a spring 9 in the open position, so that a second passage 5 between the pressure chamber 6 and a drain line 8 is open.
  • the leakage oil pressure prevails.
  • a guide diameter d 1 on the first piston 3 is equal to a slide diameter d 2 on the second piston 4.
  • the control valve 1 is constructed as a force-equalizing valve.
  • the pressure chamber 6 is connected via a line 19 with a booster piston 11 in connection.
  • the multi-stage designed booster piston 11 is connected via a Return spring 12 is held in its initial position and communicates with its smaller piston diameter with a control chamber 15 in connection.
  • the control chamber 15 is filled via a filling valve 13 and a fuel line 14 with fuel.
  • the fuel is discharged via a biased by a spring 17 injection nozzle 16 in a combustion chamber, not shown.
  • the stroke length h 2 of the slide element 3c is greater than or at least equal to the stroke length h 1 on the piston 4, it is thus ensured that there is no connection between the inlet line 7, in which high pressure prevails, and the leak oil line 8 occurs.
  • the pressure chamber 6 When the piston 3 has covered the stroke length h 2 in the direction of the pressure chamber 6, the pressure chamber 6 is in communication with the high-pressure feed line 7, so that against the force of the return spring 12, a high pressure is applied to the booster piston 11. This high pressure is transmitted due to the different diameter of the booster piston 11 to the fuel-filled control chamber 15. As a result, over the provided on the injection nozzle 16 pressure shoulder 18, the force of the spring 17 overcome and the Fuel is injected into the combustion chamber, not shown.
  • FIG. 2 a second embodiment of a valve according to the invention for controlling fluids is shown.
  • This control valve 1 can also be used in a fuel injection valve. Since the fuel injection valve of the second embodiment compared with the first embodiment has only changes to the control valve 1, has been dispensed with a representation of the other parts of the fuel injection valve in Fig. 2 and in the following description, as they are accurate as are formed in the first embodiment. Furthermore, the same reference numerals as in the first embodiment are used in the second embodiment for similar parts.
  • the control valve 1 of the second embodiment in contrast to the first embodiment, only a piston 3.
  • the piston comprises a plurality of piston sections 3a to 3e.
  • the piston 3 also has a first cylindrical piston portion 3a and a second piston portion 3b, which is concave.
  • the second piston section 3b is adjoined by a slide element 3c, which is arranged directly on the valve seat.
  • the piston 3 comprises a fourth, tapered piston portion 3d and a fifth, cylindrical piston portion 3e, which is in communication with an actuating element 2.
  • the piston 3 is partially arranged in a pressure chamber 6 and opens / closes the connection between a supply line 7 from a rail and a communicating with the pressure chamber 6 via a line 19 booster piston (not shown).
  • the control valve 1 also includes a drain line 8.
  • control valve 1 The operation of the control valve 1 according to the second embodiment is as follows.
  • the piston 3 When the actuator is actuated, the piston 3 is moved in the direction of the actuating element 2.
  • the fourth, tapered piston section 3d lifts off from the piston seat on the first passage 10.
  • the connection 10 between the high-pressure inlet line 7 and the pressure chamber 6 is opened only when the second piston section 3b facing edge of the slide element 3c has been moved past the valve seat 10.
  • the stroke length h 2 of the slider element 3c is greater than the second passage 5 provided stroke length h 1 between the first piston portion 3a and the second piston portion 3b, it is ensured that the connection between the pressure chamber 6 and the leak oil line 8 is closed before the connection via the first passage 10 between the supply line 7 and the pressure chamber 6 is opened.
  • the connection between the supply line 7 and the pressure chamber 6 is first closed before the passage 5 between the pressure chamber 6 and the drain line 8 is opened.
  • the desired coverage (h 1 -h 2 ) can be adjusted by the ratio of the stroke length h 2 of the slide element 3 c to the stroke length h 1 at the second passage 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Fluid-Driven Valves (AREA)
  • Control Of Fluid Pressure (AREA)
  • Control Of Non-Electrical Variables (AREA)
  • Safety Valves (AREA)
EP01909462A 2000-01-22 2001-01-13 Ventil zum steuern von flüssigkeiten Expired - Lifetime EP1252429B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10002702A DE10002702A1 (de) 2000-01-22 2000-01-22 Ventil zum Steuern von Flüssigkeiten
DE10002702 2000-01-22
PCT/DE2001/000122 WO2001053685A2 (de) 2000-01-22 2001-01-13 Ventil zum steuern von flüssigkeiten

Publications (2)

Publication Number Publication Date
EP1252429A2 EP1252429A2 (de) 2002-10-30
EP1252429B1 true EP1252429B1 (de) 2006-01-04

Family

ID=7628404

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01909462A Expired - Lifetime EP1252429B1 (de) 2000-01-22 2001-01-13 Ventil zum steuern von flüssigkeiten

Country Status (9)

Country Link
US (1) US6736331B2 (ja)
EP (1) EP1252429B1 (ja)
JP (1) JP2003520324A (ja)
AT (1) ATE315174T1 (ja)
CZ (1) CZ20022414A3 (ja)
DE (2) DE10002702A1 (ja)
ES (1) ES2255545T3 (ja)
HU (1) HUP0301062A2 (ja)
WO (1) WO2001053685A2 (ja)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10002702A1 (de) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10141110A1 (de) * 2001-08-22 2003-03-20 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen
JP4019934B2 (ja) * 2002-12-26 2007-12-12 株式会社デンソー 制御弁および燃料噴射弁
DE10328245A1 (de) * 2003-06-24 2005-01-13 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
CN108506130B (zh) * 2018-04-18 2024-06-11 莆田市博泰动力设备有限公司 减少高压共轨燃油动态泄漏的喷油器

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3477344A (en) * 1967-05-24 1969-11-11 United Aircraft Corp Fluid mechanical hysteretic device
DE3741526A1 (de) * 1987-12-08 1989-06-22 Bosch Gmbh Robert Sitzventil
US5241935A (en) * 1988-02-03 1993-09-07 Servojet Electronic Systems, Ltd. Accumulator fuel injection system
ES2040013T3 (es) * 1990-09-26 1993-10-01 Firma Georg Knoblauch Estuche con forma de envase plano para el almacenamiento de objetos alargados.
DE4311627B4 (de) * 1993-04-08 2005-08-25 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
US5687693A (en) * 1994-07-29 1997-11-18 Caterpillar Inc. Hydraulically-actuated fuel injector with direct control needle valve
US5680988A (en) * 1995-01-20 1997-10-28 Caterpillar Inc. Axial force indentation or protrusion for a reciprocating piston/barrel assembly
DE19701879A1 (de) * 1997-01-21 1998-07-23 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19716221B4 (de) * 1997-04-18 2007-06-21 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung mit Vor- und Haupteinspritzung bei Brennkraftmaschinen, insbesondere für schwer zündbare Kraftstoffe
DE19937713C1 (de) * 1999-08-10 2001-03-15 Siemens Ag Steuerventilanordnung zum Einsatz in einem Kraftstoffinjektor für Verbrennungsmotoren
DE10002702A1 (de) * 2000-01-22 2001-08-02 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE10031278A1 (de) * 2000-06-27 2002-01-17 Bosch Gmbh Robert Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen

Also Published As

Publication number Publication date
US20030089794A1 (en) 2003-05-15
ATE315174T1 (de) 2006-02-15
WO2001053685A3 (de) 2001-12-06
US6736331B2 (en) 2004-05-18
HUP0301062A2 (en) 2003-08-28
ES2255545T3 (es) 2006-07-01
CZ20022414A3 (en) 2004-03-17
JP2003520324A (ja) 2003-07-02
EP1252429A2 (de) 2002-10-30
WO2001053685A2 (de) 2001-07-26
DE50108611D1 (de) 2006-03-30
DE10002702A1 (de) 2001-08-02

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