WO2007098195A2 - Procédés et appareils utilisant les soupapes d'un moteur à la fois pour l'admission et pour l'échappement - Google Patents

Procédés et appareils utilisant les soupapes d'un moteur à la fois pour l'admission et pour l'échappement Download PDF

Info

Publication number
WO2007098195A2
WO2007098195A2 PCT/US2007/004501 US2007004501W WO2007098195A2 WO 2007098195 A2 WO2007098195 A2 WO 2007098195A2 US 2007004501 W US2007004501 W US 2007004501W WO 2007098195 A2 WO2007098195 A2 WO 2007098195A2
Authority
WO
WIPO (PCT)
Prior art keywords
intake
exhaust
valves
valve
manifold
Prior art date
Application number
PCT/US2007/004501
Other languages
English (en)
Other versions
WO2007098195A3 (fr
Inventor
Oded Eddie Sturman
Original Assignee
Sturman Digital Systems, Llc
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 Sturman Digital Systems, Llc filed Critical Sturman Digital Systems, Llc
Publication of WO2007098195A2 publication Critical patent/WO2007098195A2/fr
Publication of WO2007098195A3 publication Critical patent/WO2007098195A3/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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/28—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of coaxial valves; characterised by the provision of valves co-operating with both intake and exhaust ports
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/44—Multiple-valve gear or arrangements, not provided for in preceding subgroups, e.g. with lift and different valves
    • 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
    • F01L15/00—Valve-gear or valve arrangements, e.g. with reciprocatory slide valves, other than provided for in groups F01L17/00 - F01L29/00
    • F01L15/02—Valve-gear or valve arrangements, e.g. with reciprocatory slide valves, other than provided for in groups F01L17/00 - F01L29/00 with valves other than cylindrical, sleeve, or part-annularly-shaped, e.g. flat D-valves
    • F01L15/04—Valve-gear or valve arrangements, e.g. with reciprocatory slide valves, other than provided for in groups F01L17/00 - F01L29/00 with valves other than cylindrical, sleeve, or part-annularly-shaped, e.g. flat D-valves main valve being combined with auxiliary valve
    • 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
    • F01L5/00—Slide valve-gear or valve-arrangements
    • F01L5/04—Slide valve-gear or valve-arrangements with cylindrical, sleeve, or part-annularly shaped valves

Definitions

  • the present invention relates to the field of the operation and control of engine valves in piston engines.
  • the present invention is based on the fact that at higher engine speeds and higher power outputs, engines have more difficulty breathing, that is, their volumetric efficiency goes down.
  • engines may include, by way of example, two intake valves and two exhaust valves per cylinder to attempt to increase the volumetric efficiency.
  • Figure 1 is a schematic cross-section through an engine head illustrating one embodiment of the present invention.
  • Figure 2 is an embodiment similar to that of Figure 1, but using return springs for the air switch valves.
  • Figure 3 is a top schematic view of the exemplary assembly of Figure 1.
  • Figure 4 is a cross section of an embodiment using poppet valves for the air switch valves, and corresponds to a cross section taken along line A-A of Figure 3.
  • Figure 5 is another cross section of the embodiment of Figure 4, though corresponding to a cross section taken along line B-B of Figure 3.
  • FIG. 6 is a schematic diagram for a V-6 engine incorporating the present invention.
  • Figure 7 is a block diagram schematically illustrating the incorporation of the present invention in a multi- cylinder engine.
  • Figure 8 is a block diagram of a multi-cylinder engine incorporating an embodiment of the present invention, together with a fuel injector per cylinder, and a multi- cylinder engine controller.
  • the preferred embodiments of the present invention are intended to be used on diesel engines, though this is not a limitation of the invention, as the invention is also applicable to gasoline engines, or engines intended to operate on other fuels. Also, while the present invention is preferably to be used on turbocharged engines, this too is not a limitation of the invention, as the present invention is also applicable to non-turbocharged engines. Further, the preferred embodiments are intended to be used on engines having multiple intake and multiple exhaust valves, as is characteristic of most modern engines, though this too is a preference, not a limitation of the invention.
  • the present invention is intended to increase the volumetric efficiency of engines, in the exemplary embodiments disclosed herein, engines having two intake valves and two exhaust valves per cylinder, by selectively using all four valves, the two intake and the two exhaust valves, as both the intake valves and as the exhaust valves for that cylinder.
  • much larger valves external to each combustion chamber are used to switch the coupling of the valves (intake and exhaust) between an intake manifold and an exhaust manifold.
  • the intake valves may be coupled as intake valves or exhaust valves, depending on whether it is an intake stroke or an exhaust stroke.
  • the exhaust valves may be coupled between the exhaust manifold and the intake manifold, depending on whether they are then currently functioning as exhaust valves or intake valves .
  • camless engines wherein the timing and operation of the engine valves may be electronically controlled (see for instance, U.S. Patent No. 6,739,293 entitled Hydraulic Valve Actuation Systems and Methods, the disclosure of which is hereby incorporated herein by reference) . While the preferred embodiments use electronically controlled hydraulic valve actuation, other types of camless engine engine valve operation could equally as well be used. Because of that degree of control, an engine such as a diesel engine may be operated as a four cycle engine, or for higher power output, switched to two cycle operation, as desired.
  • a diesel engine may be operated as a conventional four stroke engine using two intake valves and two exhaust valves at idle and at low engine outputs , at higher engine speeds and outputs , perhaps operated with all valves functioning as both intake and exhaust valves as described, and at still higher engine outputs operating as a two stroke engine, again with all valves functioning as both intake and exhaust valves as described.
  • This is merely one example of the combinations of operating modes possible with the present invention.
  • Figure 1 presents a schematic cross-section through an engine head showing a block 20, a piston 22 and two engine valves 24.
  • These two engine valves could be either two intake valves or two exhaust valves on the respective cylinder, with two such assemblies being used per cylinder in this example.
  • Two two-way air switch valves 26 and 28 are shown, operated by electronically controlled hydraulic actuators 30 and 32 at the top of the Figure, with return pins 34 and 36 at the bottom being always subjected to hydraulic pressure for return of the air switch valves to the upper position when the hydraulic actuators 30 and/or 32 at the top of the air switch valves 26 and 28 are not pressurized.
  • At the left side is the intake manifold INT and on the right side is the exhaust manifold EXH. These manifolds would be common to all cylinders of a multi- cylinder engine .
  • the right-hand air switch valve 28 is in its upper position, preventing flow from the engine valves 24, when open, to the exhaust manifold EXH.
  • the air switch valve 26 at the left of the Figure is in its lower position, allowing flow past the engine valves 24, when open, from the intake manifold INT to the cylinder.
  • the two engine valves 24 shown with the air switch valves 26 and 28 in the position illustrated, function as intake valves.
  • the air switch valves 26 and 28 are reversed in position, the two engine valves 24 shown would function as exhaust valves.
  • Hydraulic control valve HVAl controls the two engine valves 24 for the cylinder shown, with hydraulic control valve HVA2 controlling the other two engine valves for that cylinder, not shown.
  • Hydraulic control valves SWl and SW2 control the switch valves 26 and 28 for the two engine valves 24 for the cylinder shown, with hydraulic control valves SW3 and SW4 controlling the other two switch valves for the other two engine valves for that cylinder, not shown.
  • an intensifier-type fuel injector may be used, such as one having direct needle control, and a selection of one, a second, or both intensifier actuation piston areas to provide respective intensified fuel pressures for injection, as controlled by control valves INJl, INJ2 and INJ3.
  • Figure 2 is an embodiment similar to that of Figure 1, but using return springs 42 for the air switch valves 26 and 28.
  • FIG. 3 A top schematic view of the exemplary assembly of Figure 1 is illustrated in Figure 3.
  • Two engine valves 24 are operated in unison by a single actuator 40 ( Figures 1 and 2) controlled by control valve HVAl as a result of the BRIDGE shown in Figure 1 and as illustrated in Figure 3 as vertical dashed lines extending between two engine valves 24.
  • the larger circles are the associated air switch valves 26 and 28. While in Figure 1 the air switch valves 26 and 28 are shown as a form of spool/poppet valve, any type of valve of adequate speed could be used. In that regard, note that these valves are not subjected to substantial pressure differentials, and accordingly, relatively simple valves of various configurations could be used, including but not limited to rotary valves. Also, while two, two way valves are shown, a three-way valve could be used if desired.
  • Figures 4 and 5 show schematic cross sections of an embodiment using poppet valves 26' and 28' for the air switch valves. These cross sections correspond to cross sections taken along lines A-A and B-B of Figure 3.
  • This embodiment uses hydraulic return for both the engine valves 24 and the air switch valves 26' and 28'.
  • the present invention is not limited to any form of engine valve return, or any form of air switch valves or operation thereof, provided they accommodate the desired air flow area at least as large as the combined engine valves themselves, and more preferably at least twice or three times the air flow area of the combined engine valves . It is also not limited to any form of engine valve actuation, provided the required control of engine valve operation and timing are available.
  • FIG. 6 is a diagram illustrating an embodiment on a V- 6 engine.
  • a turbocharger Turbo having a TURBINE driven from each exhaust manifold and driving an intake air COMPRESSOR is shown.
  • another Compressor driven by a hydraulic motor, augmented by a hydraulic accumulator.
  • Each cylinder of the engine includes valves INV and EXV normally functioning as intake and exhaust valves, respectively, by setting the respective air switch valves to the appropriate position and leaving them there.
  • both intake valves INV and exhaust valves EXV for any, and usually all cylinders, can be used as both intake valves and as exhaust valves whenever desired.
  • the fuel injectors normally used on such engines are not shown for clarity.
  • Figure 8 is a block diagram of a multi-cylinder engine incorporating an embodiment of the present invention, together with a fuel injector per cylinder, and a multi- cylinder engine controller.
  • the controller will respond to various inputs for control of engine valve timing, the associated switch valves and injectors based on various inputs , such as crankshaft angle and speed (measured or calculated from the changing crankshaft angle) and power setting, as well as other parameters such as intake manifold pressure, air temperature, engine temperature, etc.
  • the present invention may be used for engine compression braking, in the embodiment disclosed, using all four engine valves per cylinder to vent each cylinder when the piston is at or near top dead center. This venting may be to the exhaust manifold, or to the intake manifold to recover some of the energy of compression when braking.
  • valves are used for both intake and exhaust
  • the advantage, particularly with respect to increasing the volumetric efficiency on intake, is two-fold. First, less energy is lost by the pressure drop through the intake valves, and secondly, more air is ingested, allowing injection of greater amounts of fuel to obtain greater engine output. Thus both efficiency and maximum power output are increased.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

L'invention porte sur des procédés et appareils utilisant les soupapes d'un moteur à la fois pour l'admission et pour l'échappement et permettant de choisir le mode de fonctionnement entre le 2 temps et le quatre temps. Dans une exécution, les soupapes d'admission et d'échappement sont respectivement reliées à de petits collecteurs d'admission et d'échappement et le collecteur central peut communiquer avec l'un ou l'autre des petits collecteurs à l'aide d'une vanne à deux voies. Dans un moteur de préférence sans came, les soupapes d'admission peuvent être commandées pour fonctionner soit uniquement comme soupape d'admission soit comme soupapes d'admission ou d'échappement ou les deux, et les soupapes d'échappement soit uniquement comme soupape d'échappement soit comme soupapes d'admission ou d'échappement. Des exécutions données en exemple sont décrites.
PCT/US2007/004501 2006-02-21 2007-02-21 Procédés et appareils utilisant les soupapes d'un moteur à la fois pour l'admission et pour l'échappement WO2007098195A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US77538706P 2006-02-21 2006-02-21
US60/775,387 2006-02-21
US11/708,939 US20070215078A1 (en) 2006-02-21 2007-02-20 Methods and apparatus to use engine valves as both intake and exhaust valves
US11/708,939 2007-02-20

Publications (2)

Publication Number Publication Date
WO2007098195A2 true WO2007098195A2 (fr) 2007-08-30
WO2007098195A3 WO2007098195A3 (fr) 2007-12-27

Family

ID=38437971

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2007/004501 WO2007098195A2 (fr) 2006-02-21 2007-02-21 Procédés et appareils utilisant les soupapes d'un moteur à la fois pour l'admission et pour l'échappement

Country Status (2)

Country Link
US (1) US20070215078A1 (fr)
WO (1) WO2007098195A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103133077A (zh) * 2011-11-23 2013-06-05 韩国文 发动机双重式辅助气门
KR101511573B1 (ko) * 2014-02-11 2015-04-13 현대자동차주식회사 버스의 냉각장치
CN104196586A (zh) * 2014-09-15 2014-12-10 韩国文 发动机双重式辅助气门

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204183A (en) * 1922-08-08 1923-09-27 George Richard Inshaw An improvement in connection with the valvular arrangements of internal combustion engines
GB250095A (en) * 1925-08-26 1926-04-08 Eugenio Tosi Improvements relating to the valves and valve gear of internal combustion engines
DE697779C (de) * 1936-11-17 1940-10-23 Werke Kiel Akt Ges Deutsche Regelung von Gasmaschinen
US2323251A (en) * 1941-10-01 1943-06-29 Smith Thomas Noah Valve operating mechanism
GB2223800A (en) * 1988-07-19 1990-04-18 T & N Technology Ltd I.C. engine valve gear
WO1992014040A1 (fr) * 1991-02-07 1992-08-20 Piotr Marszalkiewicz Procede et dispositif de reglage de soupapes dans un moteur a combustion interne a quatre temps
GB2267124A (en) * 1992-04-28 1993-11-24 Harry Leslie James Dixon I.c.engine valve gear.
GB2361031A (en) * 2000-04-05 2001-10-10 Tomas Teixeira Multifunction valve i.c. piston engine
ES2176079A1 (es) * 2000-04-27 2002-11-16 Cabello Antonio Pascual Sistema de distribucion aplicable a motores.

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2439618A (en) * 1946-02-15 1948-04-13 Felix J Cloutier Combination intake and exhaust valve for four-cycle engines
US2585773A (en) * 1949-05-05 1952-02-12 Campbell Hausfeld Company Valve
US4492192A (en) * 1983-07-29 1985-01-08 Renault Vehicules Industriels Diesel piston engine
US4765293A (en) * 1986-05-07 1988-08-23 The Cessna Aircraft Company Hybrid internal combustion reciprocating engine
US4907544A (en) * 1989-04-06 1990-03-13 Southwest Research Institute Turbocharged two-stroke internal combustion engine with four-stroke capability
DE69011181T2 (de) * 1989-04-26 1994-12-08 Isuzu Ceramics Res Inst Verbrennungsmotor mit variablem Zyklus.
JPH0663458B2 (ja) * 1989-05-09 1994-08-22 いすゞ自動車株式会社 サイクル変換可能エンジン
JP2711565B2 (ja) * 1989-05-11 1998-02-10 株式会社いすゞセラミックス研究所 エンジンのサイクル制御装置
JPH04292526A (ja) * 1991-03-20 1992-10-16 Honda Motor Co Ltd ４サイクル内燃機関
EP0536513B1 (fr) * 1991-08-21 1996-07-03 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape pour moteur à combustion interne
US5619965A (en) * 1995-03-24 1997-04-15 Diesel Engine Retarders, Inc. Camless engines with compression release braking
US6223846B1 (en) * 1998-06-15 2001-05-01 Michael M. Schechter Vehicle operating method and system
US6415749B1 (en) * 1999-04-27 2002-07-09 Oded E. Sturman Power module and methods of operation
US6739293B2 (en) * 2000-12-04 2004-05-25 Sturman Industries, Inc. Hydraulic valve actuation systems and methods

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204183A (en) * 1922-08-08 1923-09-27 George Richard Inshaw An improvement in connection with the valvular arrangements of internal combustion engines
GB250095A (en) * 1925-08-26 1926-04-08 Eugenio Tosi Improvements relating to the valves and valve gear of internal combustion engines
DE697779C (de) * 1936-11-17 1940-10-23 Werke Kiel Akt Ges Deutsche Regelung von Gasmaschinen
US2323251A (en) * 1941-10-01 1943-06-29 Smith Thomas Noah Valve operating mechanism
GB2223800A (en) * 1988-07-19 1990-04-18 T & N Technology Ltd I.C. engine valve gear
WO1992014040A1 (fr) * 1991-02-07 1992-08-20 Piotr Marszalkiewicz Procede et dispositif de reglage de soupapes dans un moteur a combustion interne a quatre temps
GB2267124A (en) * 1992-04-28 1993-11-24 Harry Leslie James Dixon I.c.engine valve gear.
GB2361031A (en) * 2000-04-05 2001-10-10 Tomas Teixeira Multifunction valve i.c. piston engine
ES2176079A1 (es) * 2000-04-27 2002-11-16 Cabello Antonio Pascual Sistema de distribucion aplicable a motores.

Also Published As

Publication number Publication date
US20070215078A1 (en) 2007-09-20
WO2007098195A3 (fr) 2007-12-27

Similar Documents

Publication Publication Date Title
US6415749B1 (en) Power module and methods of operation
EP2640934B1 (fr) Moteurs à pistons opposés à deux temps à relâchement de compression pour freinage moteur
EP0643805B1 (fr) Procede et appareil de recirculation de gaz d'echappement utilisant la combustion a retour
US7500475B2 (en) Engine and method for operating an engine
EP2119888B1 (fr) Architecture séquentielle parallèle de turbocompresseur utilisant un système de levée de soupape variable de moteur à cylindre
JP2954350B2 (ja) 内燃機関の作動モードを制御する装置
EP1363001A2 (fr) Système d'alimentation d'air et de combustible pour moteur à combustion interne
US20120186249A1 (en) Turbocharged reciprocating piston engine having a connected pressure tank for bridging turbo lag, and method for operating said engine
CA2658930A1 (fr) Procede de commande de synchronisation de soupapes de moteur diesel
US20070107680A1 (en) Control apparatus and method for four-stroke premixed compression ignition internal combustion engine
WO2009092051A1 (fr) Moteurs diesel et procédés
US7124717B2 (en) Method and device for operating an internal combustion engine
US6769393B2 (en) Valve system for internal combustion engine
JP3783765B2 (ja) 過給機付きエンジンのｅｇｒ装置
JP5803326B2 (ja) 過給機付リーンバーンエンジン
JP5842406B2 (ja) 過給機付リーンバーンエンジン
US6925979B1 (en) Method of operating a multicylinder internal combustion engine
US20070215078A1 (en) Methods and apparatus to use engine valves as both intake and exhaust valves
EP1628014B1 (fr) Collecteur d'échappement
WO2005019619A1 (fr) Moteur a combustion interne et cycle de fonctionnement ameliores
US20120067311A1 (en) Method for operating an engine arrangement
US20170306869A1 (en) Diesel engine and method for starting a diesel engine
US7574982B2 (en) Engine cycles
CN108730014B (zh) 一种发动机和汽车
US7917280B2 (en) Method and device for operating an internal combustion engine

Legal Events

Date Code Title Description
NENP Non-entry into the national phase

Ref country code: DE

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07751272

Country of ref document: EP

Kind code of ref document: A2

122 Ep: pct application non-entry in european phase

Ref document number: 07751272

Country of ref document: EP

Kind code of ref document: A2