EP1504173A1 - Dispositif d'alimentation en pression pour une commande electrohydraulique de soupapes d'echange gazeux dans des moteurs a combustion - Google Patents

Dispositif d'alimentation en pression pour une commande electrohydraulique de soupapes d'echange gazeux dans des moteurs a combustion

Info

Publication number
EP1504173A1
EP1504173A1 EP02805689A EP02805689A EP1504173A1 EP 1504173 A1 EP1504173 A1 EP 1504173A1 EP 02805689 A EP02805689 A EP 02805689A EP 02805689 A EP02805689 A EP 02805689A EP 1504173 A1 EP1504173 A1 EP 1504173A1
Authority
EP
European Patent Office
Prior art keywords
valve
pump
pressure
supply device
fluid
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.)
Withdrawn
Application number
EP02805689A
Other languages
German (de)
English (en)
Inventor
Udo Diehl
Karsten Mischer
Bernd Rosenau
Juergen Schiemann
Simon Kieser
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 EP1504173A1 publication Critical patent/EP1504173A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2800/00—Methods of operation using a variable valve timing mechanism

Definitions

  • Pressure supply device for an electro-hydraulic valve control of gas exchange valves in internal combustion engines
  • the invention relates to a pressure supply device for an electrohydraulic valve control of gas exchange valves in internal combustion engines according to the preamble of claim 1.
  • the high-pressure pump is designed as a variable-pressure or suction-controlled variable displacement pump which delivers a variable pressure and a variable volume flow.
  • the variable pump lies with its pump inlet directly on the fluid reservoir and is connected with its pump outlet via a check valve with the blocking direction pointing to the pump outlet to the fluid outlet of the pressure supply device, to which a high-pressure accumulator serving for energy storage and pressure pulsation damping is connected.
  • the electrohydraulic valve control Via the fluid outlet the electrohydraulic valve control is supplied with high-pressure fluid, the distributor line or rail connected to the fluid outlet being referred to as the high-pressure circuit of the electrohydraulic valve control.
  • the electrohydraulic valve control system has to be controlled per valve 'a hydraulic actuator or valve disk having an actuating piston for actuating the valve as well as two acting on the adjusting piston, fluid-filled working chambers. All valve actuators are connected to the high-pressure distributor line or rail in such a way that the upper working chamber, which acts in the valve closing direction on a smaller effective area of the actuating piston, acts directly under the working chamber, and the upper working chamber, which acts in the valve opening direction on a larger effective area of the actuating piston, via a first electromagnetic Control valve is on the rail.
  • the upper working area of each valve actuator is additionally connected via a second electronic control valve to a second rail, which forms a return line and leads to the fluid reservoir.
  • the pressure supply device for the electrohydraulic valve control of gas exchange valves with the features of claim 1 has the advantage that the very good efficiency of the inexpensive constant pump can be used by the combination of constant pump and changeover valve between high pressure circuit and unpressurized circulation and a consumption-oriented coupling between fluid use and circulation flow is possible, so that the pressure curve in the at the fluid outlet Pressure supply device connected high-pressure rail to the electro-hydraulic valve actuators can be influenced directly.
  • a pulsation smoothing of the pressure can be brought about by deliberately superimposing the conveyance of fluid into a high-pressure accumulator connected to the fluid outlet and removing fluid from the high-pressure accumulator by the valve actuators.
  • the changeover between zero delivery rate and full delivery takes place extremely quickly in the millisecond range, in particular when the changeover valve is designed as an electrically controlled solenoid valve, so that very high system dynamics are achieved.
  • the switchover of the switchover valve can be carried out synchronously with consumption, time and / or crank angle. By switching the constant pump to unpressurized circulation during a break in delivery, constant cooling and lubrication of the constant pump by the fluid is also ensured.
  • the constant pump is self-priming and lies with its pump inlet on the fluid reservoir.
  • a fluid from the constant pump is self-priming and lies with its pump inlet on the fluid reservoir.
  • Pre-feed pump sucking in fluid reservoir must be connected upstream.
  • the oil pump of the internal combustion engine can advantageously be used as the feed pump.
  • the changeover valve is composed of a 2/2-way solenoid valve and ⁇ a check valve together.
  • the check valve is arranged in a bypass which connects the pump outlet of the constant pump with the fluid reservoir.
  • the non-return valve is connected with the blocking direction pointing to the pump outlet on the input side to the pump outlet, where the bypass also branches off, and on the outlet side to the fluid outlet, and shuts off the high pressure circuit from the bypass and the high pressure pump when the fluid is depressurized.
  • the changeover valve is designed as a 3/2-way solenoid valve, of the three valve connections of which a valve outlet is connected to the fluid outlet of the pressure supply device providing the high pressure for valve control and a valve outlet is connected to the fluid reservoir and alternately to the valve outlets switchable valve input is located at the pump outlet of the constant pump, so that, depending on the switching position of the solenoid valve, the high pressure circuit is shut off or connected to the high pressure pump.
  • Fig. 1 is a circuit diagram of a
  • Pressure supply device for valve control of gas exchange valves one
  • FIG. 2 is the same representation as in Fig. 1 according to another embodiment
  • the pressure supply device shown in the block diagram in FIG. 1 serves for the fluid supply of an electrohydraulic valve control of gas exchange valves of an internal combustion engine. - Such a valve control is described for example in DE 198 26 047 AI. to
  • valve control is connected to a fluid outlet 11 of the pressure supply device via a so-called rail, which supplies fluid, preferably hydraulic oil, to all valve actuators of the valve control.
  • the pressure supply device has a fluid reservoir 12, a prefeed pump 13, a constant pump 14 and a high pressure accumulator 15, which is connected directly to the fluid outlet 11.
  • the fluid outlet 11 is via a pressure relief valve 16, which is at the maximum permissible
  • High pressure in the high-pressure accumulator 15 is set, connected to a return line 17 leading to the fluid reservoir 12.
  • a throttle 18 is also arranged in the return line 17.
  • the prefeed pump 13 is on the suction side of the fluid reservoir 12 and is connected with its pump outlet on the one hand to the pump inlet of the constant pump 14 and on the other hand to the return line 17 upstream of the throttle 18.
  • the constant pump 14 is connected to the pump outlet via a changeover valve 19 with the high pressure accumulator 15 or the fluid outlet 11.
  • the changeover valve is included as a 3/2-way solenoid valve 20 Spring return formed, which is controlled by an electronic control unit 21 as a function of the fluid pressure prevailing at the fluid outlet 11 or in the high-pressure accumulator 15.
  • the fluid pressure is detected by means of a sensor designed as a pressure meter 22.
  • the 3/2-way solenoid valve 20 has a valve input 201 connected to the pump outlet of the constant pump 14 and two valve outputs 202, 203, to which the valve input 201 can be connected alternately depending on the switching position.
  • the valve outlet 202 is connected to the fluid outlet 11 and the high-pressure accumulator 15 and the valve outlet 203 is connected to the return line 17 on the inlet side of the throttle 18.
  • the 3/2-way solenoid valve 20 is in the switch position shown in FIG. 1, the high pressure accumulator 15 is tensioned, ie the constant pump 14 delivers fluid into the high pressure accumulator 15 until the maximum pressure set by the pressure limiting valve 16 in the high pressure accumulator 15 and at the fluid outlet 11 is reached. If the 3/2-way solenoid valve 20 is transferred from the control unit 21 into its other switching position, the fluid outlet 11 and the high-pressure accumulator 15 are blocked off from the constant pump 14, and the pump outlet of the constant pump 14 is connected to the return line 17. This results in an almost pressure-free circulation of the fluid and only as much energy is required as is necessary to overcome friction.
  • Pressure supply device is modified only with regard to the design of the changeover valve 19.
  • the other components correspond to those in Fig. 1 and are identified by the same reference numerals.
  • the changeover valve 19 has a 2/2-way solenoid valve 23 with spring return and a check valve 24.
  • the 2/2-way solenoid valve 23 has a valve inlet 231 and a valve outlet 232 which, depending on the switching position of the 2/2-way solenoid valve 23, are connected to one another or shut off from one another.
  • the valve inlet 231 is connected to the pump outlet of the constant pump 14 and the valve outlet 232 to the return line 17, so that the 2/2-way solenoid valve 23 in a fluid outlet 11 and High pressure accumulator 15 bypass 24 is located and this alternately opens or shuts off.
  • the check valve 24 is arranged between the pump outlet of the constant pump 14 and the fluid outlet 11 or high-pressure accumulator 15 with the passage direction pointing to the fluid outlet 11 or high-pressure accumulator 15.
  • the 2/2-way solenoid valve 23 switching position shown is in its 2 in Fig., The bypass 25 is blocked and the fixed displacement pump 15 conveys fluid 'in the
  • High-pressure accumulator 15 The maximum pressure that is present at the fluid outlet 11 is in turn determined by the pressure-limiting valve 16. If the 2/2-way solenoid valve 23 is switched to the other switching position against the restoring force of its return spring, the pump outlet of the constant pump 14 is connected to the return line 17 via the bypass 25 and fluid is sucked in from the fluid reservoir 12 in an unpressurized circulation and back to the fluid reservoir 12 promoted.
  • the check valve 24 'ensures that the pressure in the
  • High-pressure accumulator 15 or at the fluid outlet 11 does not collapse through the opened bypass 25.
  • a modification of the pressure supply device provides to use a pressure limiting valve 26 or a check valve 27 with a defined opening pressure instead of the throttle 18 arranged in the return line 17, as is symbolized in FIGS. 1 and 2 by the components 26, 27 shown next to the throttle 18. This can ensure a constant supply pressure to the pre-feed pump 13 and
  • the constant pump 14 is designed to be self-sucking and is directly connected to the fluid reservoir 12 with its pump inlet, so that the prefeed pump can be saved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un dispositif d'alimentation en pression pour une commande électrohydraulique de soupapes d'échange gazeux dans les moteurs à combustion interne. Ce dispositif comprend un réservoir (12) de fluide, une sortie (11) de fluide à raccorder à la commande des soupapes et une pompe haute pression qui extrait le fluide du réservoir (12) et l'achemine sous haute pression vers la sortie (11). L'invention vise à obtenir un rendement élevé de la pompe et une grande dynamique du système. A cet effet, la pompe haute pression est une pompe à cylindrée constante (14) dotée d'une entrée et d'une sortie (141, 142), la sortie (142) de la pompe pouvant être raccordée au moyen d'une soupape d'inversion (19) alternativement à la sortie (11) de fluide et au réservoir (12) de fluide lorsque la sortie (11) de fluide est obturée.
EP02805689A 2002-05-03 2002-12-12 Dispositif d'alimentation en pression pour une commande electrohydraulique de soupapes d'echange gazeux dans des moteurs a combustion Withdrawn EP1504173A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10219786A DE10219786A1 (de) 2002-05-03 2002-05-03 Druckversorgungseinrichtung für eine elektrohydraulische Ventilsteuerung von Gaswechselventilen in Brennkraftmaschinen
DE10219786 2002-05-03
PCT/DE2002/004545 WO2003093655A1 (fr) 2002-05-03 2002-12-12 Dispositif d'alimentation en pression pour une commande electrohydraulique de soupapes d'echange gazeux dans des moteurs a combustion

Publications (1)

Publication Number Publication Date
EP1504173A1 true EP1504173A1 (fr) 2005-02-09

Family

ID=29225013

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02805689A Withdrawn EP1504173A1 (fr) 2002-05-03 2002-12-12 Dispositif d'alimentation en pression pour une commande electrohydraulique de soupapes d'echange gazeux dans des moteurs a combustion

Country Status (4)

Country Link
US (1) US20040211378A1 (fr)
EP (1) EP1504173A1 (fr)
DE (1) DE10219786A1 (fr)
WO (1) WO2003093655A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7204212B2 (en) * 2005-01-12 2007-04-17 Temic Automotive Of North America, Inc. Camless engine hydraulic valve actuated system
DE102007045276A1 (de) 2007-09-21 2009-04-02 Schaeffler Kg Vorrichtung zur Ansteuerung von mindestens einem Motorventil
DE102014209856A1 (de) * 2014-05-23 2015-11-26 Volkswagen Aktiengesellschaft Hydraulische Versorgungsvorrichtung
US10113453B2 (en) * 2015-04-24 2018-10-30 Randy Wayne McReynolds Multi-fuel compression ignition engine
EP3406866A1 (fr) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
FR3071869B1 (fr) * 2017-10-02 2019-10-11 Vianney Rabhi Actionneur hydraulique de soupape a regeneration
CN111120029A (zh) * 2019-12-26 2020-05-08 哈尔滨工程大学 一种旋转柱塞式的内燃机全可变配气机构
DE102020127070A1 (de) 2020-10-14 2022-04-14 Fte Automotive Gmbh Pumpenaggregat zur Kuppplungsbetätigung

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992007174A1 (fr) * 1990-10-16 1992-04-30 Lotus Cars Ltd. Appareil de commande de soupape
US6308690B1 (en) * 1994-04-05 2001-10-30 Sturman Industries, Inc. Hydraulically controllable camless valve system adapted for an internal combustion engine
US5562070A (en) * 1995-07-05 1996-10-08 Ford Motor Company Electrohydraulic camless valvetrain with rotary hydraulic actuator
DE19816817A1 (de) * 1997-11-25 1999-10-21 Bayerische Motoren Werke Ag Hydraulische Betätigungsvorrichtung für ein Gaswechselventil einer Brennkraftmaschine
DE19854891C2 (de) * 1997-11-28 2003-02-06 Aisin Seiki Ventilzeitsteuervorrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO03093655A1 *

Also Published As

Publication number Publication date
DE10219786A1 (de) 2003-11-13
US20040211378A1 (en) 2004-10-28
WO2003093655A1 (fr) 2003-11-13

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