GB2185286A - I.C. engine with an exhaust gas driven turbine or positive displacement expander - Google Patents
I.C. engine with an exhaust gas driven turbine or positive displacement expander Download PDFInfo
- Publication number
- GB2185286A GB2185286A GB08600620A GB8600620A GB2185286A GB 2185286 A GB2185286 A GB 2185286A GB 08600620 A GB08600620 A GB 08600620A GB 8600620 A GB8600620 A GB 8600620A GB 2185286 A GB2185286 A GB 2185286A
- Authority
- GB
- United Kingdom
- Prior art keywords
- engine
- exhaust
- exhaust valve
- internal combustion
- dual mode
- 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- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B21/00—Combinations of two or more machines or engines
- F01B21/04—Combinations of two or more machines or engines the machines or engines being not all of reciprocating-piston type, e.g. of reciprocating steam engine with steam turbine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/10—Engines with prolonged expansion in exhaust turbines
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The outlets of cylinder valves 11 and 13 or parts of a two-stroke or rotary piston engine which open one after the other are connected respectively to a power extraction device 15 and an unobstructed outlet 14. Overlap may exist between the opening of the valves and their timing may be variable. <IMAGE>
Description
SPECIFICATION
Dual mode exhaust valve system
This invention relates to a dual mode exhaust valve system on an internal combustion engine.
Devices for converting the heat energy in the exhaust gases of internal combustion engines to mechanical power are well known. These devices can taketheform of gas dynamic machines such as turbines or positive displacement machines such as screw expanders. The mechanical power extracted may be used forvarious purposes such as driving superchargers or contributing to engine shaft output power.
It is a characteristic of these devices that a pressure ratio must exist across the device in order to provide power and thatfor each particular device there is an ideal pressure ratio.This pressure ratio is available due to the fact that the host internal combustion engine exhaustvalves open before the hot gases within the cylinderhave been expanded down to atmospheric pressure.
The exha ust va Ive open ing point may be chosen to provide more or less pressure as required. Once the exhaust valves of the host engine have been opened towards the latter part of the power stroke they are kept open during the exhaust or scavenge period in order to allow the spent gases to be expelled from the working cylinder.
Howeverthis current arrangement has two undesirable effects. viz.
The exhaust energy power extraction device system must be sized to handle the complete engine gas flow.
The passage of the low pressure scavenge exhaust gases through the power extraction device is restricted by the device and bythe presence of high pressure gas from other cylinders which may be present in the device during the scavenge period.
Ideally there should be no restriction to gas flow during the working cylinderscavenging process or power may be lost
Atypical example of current engine and exhaust energy recovery systems is shown in Fig 1 in which 1 is the engine working cylinder, 2 is the inlet valve, 3 is the exhaust valve, 4 is the exhaust energy power extraction device, 5 is the exhaust system and 6 is an optional bypass valve.
According to the present invention on an internal combustion engine fitted with an exhaust energy mechanical power extraction device, (such as a turbine or screw expander) there is provided a dual mode exhaust valve system having an auxiliary exhaust valve or valves arranged to open at a point during theengine powerstrokewhen the engine cylinder pressure is at optimum level to operate the exhaust energy power extraction device and to close atsome pre-determinedtime when the cylinder pressure has dropped to a point below which the exhaust energy mechanical power extraction device can no longer usefully extract power, the said auxiliary valve(s) port being connected to the exhaust energy power extraction device, and a main exhaust valve or valves arranged to open at or close to the closing point of the auxiliary valve(s) andto remain open during the scavenge period ofthe engine, the said main exhaust valve(s) and port being used to scavengethe engine cylinder of exhaust gases via an unobstructed duct.
A specific embodiment of the invention will now be described by way of example with reference to the accompanying drawings in which Figure 2 shows in diagramaticform the layout of the exhaust valve system.
Figure 3 illustrates typical valve timing for the dual mode exhaust valve system applied to a four stroke engine cycle.
Figure 4 illustrates typical valvetiming forthe dual mode exhaustvalve system applied to a two stroke engine cycle.
Referring to the drawings an engine fitted with the dual mode exhaust valve system comprises an engine 7, into the cylinder head ofwhich is fitted an inlet valve 8 or valves allowing working cylinder 9 to communicatewith inlet port 10. An auxiliaryexhaustvalve 11 allowing working cylinder 9 to communicate with auxiliary exhaust port 12 and a scavenge exhaust valve 13 allowing the working cylinderto communicatewith exhaust duct 14.
The auxiliary exhaust port 12 is connected to exhaust energy mechanical power extraction device 15 which in turn exhausts into outlet duct 16 ultimately leading to exhaust system 17.
Air or airfuel mixture is drawn orforced into the engine working cylinder9 via port 10 and valve(s) 8 as is normal. Typical opening and closing pointsforthe inlet valves or ports on 4stroke and 2 stroke engines are shown by points 18 and 19 stroke) and 28 and 29 (2 stroke).
The air orairfuel mixture is compressed and in the case of a compression ignition engine fuel is injected and ignited and in the case of a spark ignition engine the airfuel mixture is ignited by spark as normal.
At some point 20 (4 stroke) or 24(2 stroke) during the power or expansion stroke when the cylinder pressure has dropped to a value suitable for supplying to the exhaust energy power extraction device 15 the auxiliaryvalve 11 is opened allowing pressurised gas to flow via port 1 2 to device 1 5. Wh en the cyl i nder pressure has dropped to a point below which device 15 can no longer usefully extract any more power, then valve 11 is ciosed(Point21 on the4stroke diagram and 25 on the 2 stroke diagram) and Valve 13 is opened (point 22 on the 4 stroke diagram and 26 on the 2 stroke diagram) to allow scavenging of the spent gases from the working cylinders 9 via port 14to exhaust system 17. Valve 13 would typically close at point 23 (4 stroke) and 27 (2 stroke). The scavenging process does not therefore suffer any unnecessary restriction and the exhaust energy power extraction device need only be sized to caterfor part ofthe engine total gas flow.
The letters TDC and BDC in Fig 3 and 4 are abbreviations for Top Dead Centre and Bottom Dead
Centre and refer to the crank angle positions corresponding to piston in theclearancevolume position in the cylinder and in the maximum volume position respectively.
The exhaust energy power extraction device may be fitted with a bypass valve 6 which can be openedto reduce the pressure ratio across the power extraction device if necessary as on current known devices.
Claims (6)
1. On an internal combustion engine fitted with an exhaust energy mechanical power extraction device (such as turbine or screw expander) there is provided a dual mode exhaust valve system having an auxiliary exhaust valve or valves arranged to open at a point during the engine power stroke when the engine cylinder pressure is at an optimum level to operate the exhaust energy power extraction device and to close at some pre-determined time, when the cylinder pressure has dropped to a point below which the exhaust energy power extraction device can no longer usefully extract power, the said auxiliary valve(s) port being connected to the exhaustenergypowerextrac tion device, anda main exhaustvalve or valves arranged to open atorclose to the closing point of the auxiliary valve(s) and to remain open during the scavenge period ofthe engine, the said main exhaust valve(s) and port being used to scavenge the engine cylinder of exhaust gases via an unobstructed duct
2. An internal combustion engine provided with a dual mode exhaust valve system as in claim 1 wherebythe auxiliary valve closing point and main exhaust valve opening point overlap.
3. An internal combustion engine provided with a dual mode exhaust valve system as in claims 1 & 2 wherebythe engine is a two stroke engine and the exhaust valves are openings in the side ofthe cylinder which become exposed due to piston movement during the engine operation.
4. An internal combustion engine provided with a dual mode exhaustvalve system as in claims 1 & 2 whereby the engine is ofthe rotary piston type and the exhaustvalvesare openings in the perimeter ofthe piston enclosure which become exposed due to piston rotation during the engine operations.
5. An internal combustion engine provided with a dual mode exhaust valve system as in claims 1,2,3 or 4wherebythe auxiliary and or main exhaust valve opening and ciosingtiming can be altered whilst the engine is running
6. An internal combustion engine provided with a dual mode exhaustvalve system as in claims 1,2,3,4 or 5 whereby the exhaustenergy power extraction device is fitted with a bypass valve which may be opened to reducethe pressure ratio across the power extraction device.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08600620A GB2185286A (en) | 1986-01-11 | 1986-01-11 | I.C. engine with an exhaust gas driven turbine or positive displacement expander |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB08600620A GB2185286A (en) | 1986-01-11 | 1986-01-11 | I.C. engine with an exhaust gas driven turbine or positive displacement expander |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB8600620D0 GB8600620D0 (en) | 1986-02-19 |
| GB2185286A true GB2185286A (en) | 1987-07-15 |
Family
ID=10591230
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08600620A Withdrawn GB2185286A (en) | 1986-01-11 | 1986-01-11 | I.C. engine with an exhaust gas driven turbine or positive displacement expander |
Country Status (1)
| Country | Link |
|---|---|
| GB (1) | GB2185286A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994007010A1 (en) * | 1992-09-11 | 1994-03-31 | Saab Automobile Aktiebolag | Exhaust gas flow system for an internal combustion engine fitted with a supercharger, and method used for such a system |
| WO2000020745A1 (en) * | 1998-10-05 | 2000-04-13 | Saab Automobile Ab | Method of operating an internal-combustion engine, and internal-combustion engine |
| WO2001020136A1 (en) * | 1999-09-15 | 2001-03-22 | Saab Automobile Ab | Internal combustion engine |
| WO2002079624A1 (en) * | 2001-03-30 | 2002-10-10 | Saab Automobile Ab | Method for controlling the charging pressure at a turbocharged combustion engine, and a corresponding combustion engine |
| FR2860834A1 (en) * | 2003-10-08 | 2005-04-15 | Inst Francais Du Petrole | Overfed internal combustion engine, has cylinder that is provided with additional exhaust unit with additional exhaust tube and additional exhaust valve that has section permitting evacuation of different quantities of exhaust gas |
| US7104060B2 (en) * | 2001-11-02 | 2006-09-12 | Toyota Jidosha Kabushiki Kaisha | Exhaust energy recovery system for combustion engine |
| WO2009030694A2 (en) | 2007-09-05 | 2009-03-12 | Mahle International Gmbh | Piston engine |
| GB2457326A (en) * | 2008-10-17 | 2009-08-12 | Univ Loughborough | Internal combustion engine exhaust arrangement with reduced pumping losses |
| US8065878B2 (en) | 2008-03-10 | 2011-11-29 | Deere & Company | Two phase exhaust for internal combustion engine |
| US9086011B2 (en) | 2010-01-22 | 2015-07-21 | Borgwarner Inc. | Directly communicated turbocharger |
| EP3555443A4 (en) * | 2016-12-15 | 2020-07-22 | JANHUNEN, Timo | Internal combustion engine and method of operating an internal combustion engine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB179926A (en) * | 1921-05-14 | 1923-05-10 | Rateau Soc | Improvements in or relating to internal combustion engines |
| GB221011A (en) * | 1923-06-02 | 1924-09-02 | William Beardmore | Improvements in or relating to internal combustion engines operating on the two-stroke cycle |
| GB354242A (en) * | 1929-01-30 | 1931-07-30 | Armando Levi Cases | A plant for employing the exhaust gases of internal combustion engines |
| GB536794A (en) * | 1940-06-03 | 1941-05-28 | George Stephen Kammer | Improvements in two-stroke sleeve valve engines |
| GB882516A (en) * | 1959-09-16 | 1961-11-15 | Ceskoslovenske Zd Y Naftovych | Improvements in supercharged reciprocating internal combustion engines |
-
1986
- 1986-01-11 GB GB08600620A patent/GB2185286A/en not_active Withdrawn
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB179926A (en) * | 1921-05-14 | 1923-05-10 | Rateau Soc | Improvements in or relating to internal combustion engines |
| GB221011A (en) * | 1923-06-02 | 1924-09-02 | William Beardmore | Improvements in or relating to internal combustion engines operating on the two-stroke cycle |
| GB354242A (en) * | 1929-01-30 | 1931-07-30 | Armando Levi Cases | A plant for employing the exhaust gases of internal combustion engines |
| GB536794A (en) * | 1940-06-03 | 1941-05-28 | George Stephen Kammer | Improvements in two-stroke sleeve valve engines |
| GB882516A (en) * | 1959-09-16 | 1961-11-15 | Ceskoslovenske Zd Y Naftovych | Improvements in supercharged reciprocating internal combustion engines |
Cited By (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1994007010A1 (en) * | 1992-09-11 | 1994-03-31 | Saab Automobile Aktiebolag | Exhaust gas flow system for an internal combustion engine fitted with a supercharger, and method used for such a system |
| US6438956B1 (en) | 1998-10-05 | 2002-08-27 | Saab Automobile Ab | Method of operating an internal-combustion engine, and internal-combustion engine |
| WO2000020745A1 (en) * | 1998-10-05 | 2000-04-13 | Saab Automobile Ab | Method of operating an internal-combustion engine, and internal-combustion engine |
| DE10084965B3 (en) * | 1999-09-15 | 2011-12-08 | Saab Automobile Ab | internal combustion engine |
| WO2001020136A1 (en) * | 1999-09-15 | 2001-03-22 | Saab Automobile Ab | Internal combustion engine |
| US6595183B1 (en) | 1999-09-15 | 2003-07-22 | Saab Automobile Ab | Internal combustion engine |
| US6883319B2 (en) | 2001-03-30 | 2005-04-26 | Saab Automobile Ab | Method for controlling the charging pressure at a turbocharged combustion engine, and a corresponding combustion engine |
| WO2002079624A1 (en) * | 2001-03-30 | 2002-10-10 | Saab Automobile Ab | Method for controlling the charging pressure at a turbocharged combustion engine, and a corresponding combustion engine |
| DE10297129B4 (en) * | 2001-03-30 | 2010-10-21 | Saab Automobile Ab | Method for controlling the boost pressure of a turbocharged internal combustion engine and associated internal combustion engine |
| US7104060B2 (en) * | 2001-11-02 | 2006-09-12 | Toyota Jidosha Kabushiki Kaisha | Exhaust energy recovery system for combustion engine |
| FR2860834A1 (en) * | 2003-10-08 | 2005-04-15 | Inst Francais Du Petrole | Overfed internal combustion engine, has cylinder that is provided with additional exhaust unit with additional exhaust tube and additional exhaust valve that has section permitting evacuation of different quantities of exhaust gas |
| WO2009030694A2 (en) | 2007-09-05 | 2009-03-12 | Mahle International Gmbh | Piston engine |
| WO2009030694A3 (en) * | 2007-09-05 | 2009-06-18 | Mahle Int Gmbh | Piston engine |
| US8857177B2 (en) | 2007-09-05 | 2014-10-14 | Mahle International Gmbh | Piston engine |
| US8065878B2 (en) | 2008-03-10 | 2011-11-29 | Deere & Company | Two phase exhaust for internal combustion engine |
| GB2457326B (en) * | 2008-10-17 | 2010-01-06 | Univ Loughborough | An exhaust arrangement for an internal combustion engine |
| JP2012505994A (en) * | 2008-10-17 | 2012-03-08 | ラフバラ・ユニバーシティ | Exhaust structure for engine |
| US8539770B2 (en) | 2008-10-17 | 2013-09-24 | Loughborough University | Exhaust arrangement for an internal combustion engine |
| GB2457326A (en) * | 2008-10-17 | 2009-08-12 | Univ Loughborough | Internal combustion engine exhaust arrangement with reduced pumping losses |
| US9086011B2 (en) | 2010-01-22 | 2015-07-21 | Borgwarner Inc. | Directly communicated turbocharger |
| US10215084B2 (en) | 2010-01-22 | 2019-02-26 | Borgwarner Inc. | Directly communicated turbocharger |
| EP3555443A4 (en) * | 2016-12-15 | 2020-07-22 | JANHUNEN, Timo | Internal combustion engine and method of operating an internal combustion engine |
| US10947891B2 (en) | 2016-12-15 | 2021-03-16 | Timo Janhunen | Internal combustion engine and method of operating an internal combustion engine |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8600620D0 (en) | 1986-02-19 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |