WO1993001399A1 - Systeme de soupape de moteur a recuperation et son procede de fonctionnement - Google Patents

Systeme de soupape de moteur a recuperation et son procede de fonctionnement Download PDF

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Publication number
WO1993001399A1
WO1993001399A1 PCT/US1991/007451 US9107451W WO9301399A1 WO 1993001399 A1 WO1993001399 A1 WO 1993001399A1 US 9107451 W US9107451 W US 9107451W WO 9301399 A1 WO9301399 A1 WO 9301399A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure fluid
high pressure
plunger surface
fluid
Prior art date
Application number
PCT/US1991/007451
Other languages
English (en)
Inventor
J. Roger Weber
Original Assignee
Caterpillar Inc.
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 Caterpillar Inc. filed Critical Caterpillar Inc.
Priority to DE69114509T priority Critical patent/DE69114509T2/de
Priority to EP92900062A priority patent/EP0548294B1/fr
Priority to JP04500684A priority patent/JP3121011B2/ja
Publication of WO1993001399A1 publication Critical patent/WO1993001399A1/fr

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

Definitions

  • the present invention relates generally to the method of operation of hydraulically-actuated valves, and more particularly to a method of operation which significantly reduces the energy consumption normally associated with hydraulically actuated valves by recuperating some of the energy used in pressurizing the hydraulic fluid.
  • Hydraulically actuated engine valves are advantageous over mechanically actuated engine valves because they are capable of varying and thereby optimizing the timing of engine valve opening and closing events in rapid response to varying engine operating conditions.
  • the present invention is for recuperating some of the energy used in pressurizing the hydraulic fluid so that the energy requirements for hydraulic hydraulic valve systems will be comparable to mechanical valve systems.
  • an energy recuperative valve system comprising a valve, a source of relatively low pressure fluid, a source of relatively high pressure fluid, and a selective fluid communication means.
  • the valve is displaceable between a closed position and an open position and has a plunger surface.
  • the selective fluid communication means is provided for selectively communicating fluid between the plunger surface and either the low pressure fluid source or the high pressure fluid source.
  • the plunger surface is operable to urge the valve towards the open position when in communication with the high pressure fluid and is also operable to return the fluid under pressure to the high pressure fluid source when the valve moves from the open position towards the closed position, thus recuperating some of the energy used to originally pressurize the fluid.
  • a method of operating a hydraulically-actuated valve system comprises the steps of communicating fluid from a low pressure fluid source to the plunger surface of a valve during a first portion of displacement of the valve from its open position towards its closed position and then communicating fluid from a high pressure fluid source to the plunger surface during a second portion of displacement of the valve from its open position towards its closed position.
  • the present invention reduces the hydraulic power consumption normally associated with hydraulically actuated valve systems by recuperating a portion of the energy used to pressurize the hydraulic fluid. Moreover, the velocity of the valve can be controlled while it is opening so that it does not overshoot its equilibrium position when fully opened. Furthermore, the velocity of the valve can be controlled while it is closing so that the valve gently abuts against its seat. Finally, the present invention enables the valve to be opened and closed at the most appropriate times to help optimize engine performance.
  • Fig. 1 is a diagrammatic partial cross-sectional view of an electro-hydraulic valve system of the present invention.
  • Fig. 2 shows three diagrammatic exemplary graphs that illustrate an exemplary operation of the system of Fig. 1.
  • the bottom graph shows microprocessor logic pulse in terms of voltage "v” as a function of time “t” .
  • the middle graph shows spool valve displacement "d " as a function of time "t”.
  • the top graph shows engine valve displacement "d” as a function of time "t".
  • FIG. 1 there is shown an exemplary embodiment of an engine valve system 10 of the present invention for an internal combustion engine.
  • the system 10 includes one or more engine valve(s) 12 each displaceable between a first closed position (shown) and a second open position (not shown) , a plunger 14 integrally formed with or separately positioned adjacent to each engine valve 12 having a plunger surface 16, first means, preferably a pair of helical compression springs 18, for biasing each engine valve 12 towards its first position, a source 20 of relatively low pressure fluid, a source 22 of relatively high pressure fluid, second means, preferably a second valve, preferably a two-way spool valve 24 for selectively communicating fluid through a rail 25 between one of the low pressure fluid source 20 or the high pressure fluid source 22 and the plunger surface 16.
  • first means preferably a pair of helical compression springs 18, for biasing each engine valve 12 towards its first position
  • second means preferably a second valve, preferably a two-way spool valve 24 for selectively communicating fluid through a rail 25 between one of the low pressure fluid source 20 or the high pressure fluid source 22 and the plunger surface 16.
  • the spool valve 24 is biased to a first position (shown) by a helical compression spring 26 and moved against the force of the spring 26 to a second position (not shown) to the right of the first position by an actuator.
  • the actuator is a piezoelectric motor 28. Adjacent the piezoelectric motor is a relatively large diameter piston 30, and spring biased array which is in hydraulic communication with a relatively small diameter piston 32, which is adjacent the spool valve 24.
  • the large 30 and small 32 pistons are spring biased away from each other.
  • the engine valves 12 are only partially shown in Fig. 1 and may, for example, be a set of conventional exhaust or intake poppet valves that are reciprocally disposed in a cylinder head 34.
  • the plunger 16 is reciprocally guided in a bore 36 of a valve body 38.
  • the fluid pressure of the fluid from the low pressure fluid source 20 is preferably less than 400 psi, and more preferably less than 200 psi. It is recommended that enough pressure be maintained in the low pressure fluid source so that there will be little if any cavitation in the ratil 25 and at the plunger surface 16 when switching from high pressure fluid to low pressure fluid, as is later explained.
  • the fluid pressure of the fluid from the high pressure fluid source 22 is preferably greater than 1500 psi, and more preferably greater than 3000 psi.
  • the following sequence begins with the engine valve 12 at its first position, which is its closed or seated position, as shown by A. in the top graph of Fig. 2, and the spool valve at its first position, as shown by P L in the middle graph of Fig. 2.
  • a voltage V bland is sent to the piezoelectric motor 28.
  • the piezoelectric motor 28 expands, thus driving the large piston 30, which through hydraulic communication drives the small piston 32, which in turn drives the spool valve 24 from its first position P L to its second position P curatri.
  • the high pressure fluid is great enough to cause the engine valve 12 to open against the force of the compression springs 18.
  • Communication of the high pressure source 22 with the plunger surface 16 is maintained during a first portion of displacement of the engine valve 12 from A- to A_ until sufficient momentum is built up in the engine valve 12 so that it will coast to full open.
  • the piezoelectric motor 28 is again energized, again forcing the spool valve 24 to its second position P réelle, thus switching the fluid in communication with the plunger surface 16 from low pressure to high pressure. In this manner, the engine valve 12 is able to be maintained open against the force of the compression springs 18. Between t_ and t., the velocity of the engine valve is zero. The engine valve 12 is held open in this manner until the appropriate time t. in the engine cycle for it to close.
  • the voltage is removed from the piezoelectric motor 28 allowing the spool valve 24 to return from its second position P réelle to its first position P L thus switching the fluid in communication with the plunger surface 16 from high pressure to low pressure, thereby allowing the engine valve 12 to begin its closing stroke.
  • the potential energy of the compression springs 18 is turned into kinetic energy in the moving engine valve 12.
  • the low pressure fluid supply 20 is maintained in communication with the plunger surface 16 until there is sufficient momentum to close the engine valve 12 against relatively high pressure fluid.
  • the piezoelectric motor 28 is again energized, moving the spool valve 24 from its first position P J ⁇ _ to its second position P réelleii, thus switching the fluid in communication with the plunger surface 16 from low pressure to high pressure. Because enough momentum is in the engine valve 12 to carry it to its closed position A,, against the force of the high pressure fluid, the plunger 14 now acts like a fluid pump by returning fluid under pressure to the high pressure source 22 as the valve moves from A. _.• to A g . This is the hydraulic energy recuperation portion of the cycle. Analytically, the kinetic energy of the engine valve 12 is converted into potential energy in the high pressure fluid source 22.
  • the piezoelectric motor 28 is deenergized and the spool valve 24 moves from its second position P réelle _ ⁇ to its first position P.., thus switching the fluid in communication with the plunger surface 16 from high pressure to low pressure, otherwise the engine valve 12 would begin to open again.
  • the cycle is now ready to be repeated.
  • the recuperative valve system of the present invention has several advantages.
  • First, the system is able to selectively turn “on” or “off” fluid communication between the high pressure source 22 and the plunger surface 16 depending upon the position of the engine valve 12 so that hydraulic power consumption is minimized.
  • Second, the displacement of the engine valve 12 in the opening direction is controlled so that the the engine valve 12 does not overshoot its equilibrium position at full open.
  • Third, the displacement of the engine valve 12 in the closing direction is controlled so that valve seating velocity is minimized.
  • Fourth, the system is capable of opening and closing the engine valve 12 at the most appropriate times in order to help optimize engine performance. Fifth, hydraulic energy is saved and recuperated during the coasting phases of the engine valve 12 thereby reducing the energy requirements of the system.

Landscapes

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

Abstract

Système (10) de soupape de moteur à récupération destiné à un moteur à combustion interne. Ledit système comprend une soupape de moteur (12) comportant une surface de piston (16), un premier dispositif (20) servant à solliciter la soupape de moteur (12) pour qu'elle se ferme, une source de fluide (22) dont la pression est relativement basse, une source de fluide (24) dont la pression est relativement élevée, et un deuxième dispositif (28) servant sélectivement à faire circuler le fluide entre la surface de piston (16) et une des deux sources de fluide (22 et 24) à basse et à haute pressions. La durée de la circulation sélective du fluide à basse pression et du fluide à haute pression vers la surface de piston (16) pendant le déplacement de la soupape est commandée de manière à économiser et à récupérer l'énergie.
PCT/US1991/007451 1991-07-12 1991-10-10 Systeme de soupape de moteur a recuperation et son procede de fonctionnement WO1993001399A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE69114509T DE69114509T2 (de) 1991-07-12 1991-10-10 Verfahren zur betätigung einer hubventilvorrichtung mit rückgewinnung.
EP92900062A EP0548294B1 (fr) 1991-07-12 1991-10-10 Procede de commande d'un syteme de soupape avec recuperation
JP04500684A JP3121011B2 (ja) 1991-07-12 1991-10-10 回復式エンジンバルブシステム及びその操作方法

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US72913891A 1991-07-12 1991-07-12
US729,138 1991-07-12

Publications (1)

Publication Number Publication Date
WO1993001399A1 true WO1993001399A1 (fr) 1993-01-21

Family

ID=24929747

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1991/007451 WO1993001399A1 (fr) 1991-07-12 1991-10-10 Systeme de soupape de moteur a recuperation et son procede de fonctionnement

Country Status (5)

Country Link
EP (1) EP0548294B1 (fr)
JP (1) JP3121011B2 (fr)
AU (1) AU9017291A (fr)
DE (1) DE69114509T2 (fr)
WO (1) WO1993001399A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0767295A1 (fr) * 1995-10-03 1997-04-09 New Sulzer Diesel Ag Commande de soupape hydraulique
EP0830496A1 (fr) * 1995-05-17 1998-03-25 Sturman Industries, Inc. Actionneur hydraulique pour moteur thermique
EP1191193A1 (fr) * 2000-09-22 2002-03-27 MAGNETI MARELLI POWERTRAIN S.p.A. Moteur à combustion interne pour véhicule
EP1260680A2 (fr) 2001-05-22 2002-11-27 Caterpillar Motoren GmbH & Co. KG Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel
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
EP3656990A1 (fr) 2018-11-22 2020-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
WO2021121639A1 (fr) 2019-12-20 2021-06-24 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique pour des constituants d'accélération et de freinage qui doivent être déplacés de manière dynamique

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2063075A1 (fr) * 2007-11-23 2009-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Commande de soupape entraînée par fluide

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0139566A1 (fr) * 1983-09-23 1985-05-02 Societe Alsacienne De Constructions Mecaniques De Mulhouse Bloc électro-hydraulique de commande des soupapes pour moteur à combustion interne

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4899700A (en) * 1988-02-08 1990-02-13 Magnavox Government And Electronic Company Pneumatically powered valve actuator

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0139566A1 (fr) * 1983-09-23 1985-05-02 Societe Alsacienne De Constructions Mecaniques De Mulhouse Bloc électro-hydraulique de commande des soupapes pour moteur à combustion interne

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 009, no. 051 (M-361)6 March 1985 & JP,A,59 188 016 ( HITACHI ZOSEN KK ) 25 October 1984 *
PATENT ABSTRACTS OF JAPAN vol. 9, no. 229 (M-413)(1952) 14 September 1985 & JP,A,60 085 209 ( KAWASAKI JUKOGYO KK ) 14 May 1985 *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0830496A1 (fr) * 1995-05-17 1998-03-25 Sturman Industries, Inc. Actionneur hydraulique pour moteur thermique
EP0830496A4 (fr) * 1995-05-17 1999-01-13 Sturman Ind Inc Actionneur hydraulique pour moteur thermique
EP0767295A1 (fr) * 1995-10-03 1997-04-09 New Sulzer Diesel Ag Commande de soupape hydraulique
CN1088145C (zh) * 1995-10-03 2002-07-24 瓦特西拉瑞士有限公司 液压阀门驱动装置
EP1191193A1 (fr) * 2000-09-22 2002-03-27 MAGNETI MARELLI POWERTRAIN S.p.A. Moteur à combustion interne pour véhicule
US6510825B2 (en) 2000-09-22 2003-01-28 Magneti Marelli Powertrain S.P.A. Internal combustion engine for motor vehicles and the like
DE10124869A1 (de) * 2001-05-22 2002-12-12 Caterpillar Motoren Gmbh & Co Hydraulische Steuereinrichtung für wenigstens ein Hubventil einer Brennkraftmaschine
EP1260680A2 (fr) 2001-05-22 2002-11-27 Caterpillar Motoren GmbH & Co. KG Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel
DE10124869C2 (de) * 2001-05-22 2003-06-26 Caterpillar Motoren Gmbh & Co Hydraulische Steuereinrichtung für gleichwirkende Motorventile eines Dieselmotors
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
WO2018215335A1 (fr) 2017-05-22 2018-11-29 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique permettant d'accélérer et de décélérer des composants à déplacer de manière dynamique
EP3656990A1 (fr) 2018-11-22 2020-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
WO2021121639A1 (fr) 2019-12-20 2021-06-24 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique pour des constituants d'accélération et de freinage qui doivent être déplacés de manière dynamique

Also Published As

Publication number Publication date
DE69114509T2 (de) 1996-07-04
DE69114509D1 (de) 1995-12-14
EP0548294A1 (fr) 1993-06-30
JPH06501081A (ja) 1994-01-27
JP3121011B2 (ja) 2000-12-25
AU9017291A (en) 1993-02-11
EP0548294B1 (fr) 1995-11-08

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