EP2198129B1 - Desmodromic variable valve actuation - Google Patents
Desmodromic variable valve actuation Download PDFInfo
- Publication number
- EP2198129B1 EP2198129B1 EP08763225A EP08763225A EP2198129B1 EP 2198129 B1 EP2198129 B1 EP 2198129B1 EP 08763225 A EP08763225 A EP 08763225A EP 08763225 A EP08763225 A EP 08763225A EP 2198129 B1 EP2198129 B1 EP 2198129B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- track
- link
- pivot
- desmodromic
- 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.)
- Not-in-force
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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
- F01L1/30—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of positively opened and closed valves, i.e. desmodromic 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
- F01L13/0026—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio by means of an eccentric
-
- 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
Definitions
- the swivel joint is actuated positively in both directions by a link having a drive pin mounted at one end, the drive pin being engaged in a track to reciprocate therein.
- the resulting valve mechanism is rid of restoring springs of any kind, it operates reliably at racing revs because it is rid of heavy fast moving parts like the track, and it is fully variable: it can change continuously and independently the valve duration arid the valve lift from a maximum value to even zero, i.e.
- VVA variable valve actuation
- US4,898,130 and US35,016,581 Jaguar - Parsons patents, wherein a rotating eccentric pin drives, via a link, a drive pin engaged in a track formed on a rocker arm.
- Desmodromic VVAs are also described in US6,053,134 (Linebarger), in PCT/US2006/026429 (Decuir), in PCT/AU1998/000090 (Armstrong) etc.
- Fig 1 shows a preferred embodiment.
- Fig 2 shows a simplified Lost Motion version. This embodiment does not correspond to embodiments in accordance with this invention.
- Fig 3 shows, from two different points of view, a desmodromic fully variable valve actuation mechanism applied on a pair of valves.
- Figs 4 to 10 show the mechanism of Fig 3 after the removal of some parts to reveal the inner parts.
- Fig 11 shows some details of the mechanism of Fig 3 .
- Fig 12 shows another embodiment. This embodiment does not correspond to embodiments in accordance with this invention.
- Fig 13 shows at top a mechanical valve lash adjuster and at bottom a hydraulic valve lash adjuster.
- Fig 14 shows the mechanism of Fig 1 simplified.
- Figs 15 to 18 show obvious modifications of the basic mechanism of Fig 1 . These embodiments do not correspond to embodiments in accordance with this invention.
- Fig 19 shows the application of the valve mechanism in a Vee engine.
- Fig 20 shows the variability of the various valve trains in a lift-duration plot.
- Fig 21 shows the basic parts of a prototype cylinder head exhibited at international Engine Expo 2008, May 6 to 8, Stuttgart, Germany, details at www.pattakon.com
- FIG. 1 shows, in cross-section, a cylinder head with an inlet valve 11 slidably located in a valve guide.
- the valve 11 comprises a valve stem and a valve head, the latter being arranged to engage against a valve seat to close a port.
- a valve actuator 10 is slidably fitted in a guide 101.
- Means, like nut 112, lash adjustment washer 114 and elastic washer 113 are also provided to accommodate the valve lash adjustment and the thermal expansion and to assure the sealing of the valve against its seat when the valve is closed.
- a track 4 is provided having a lost motion portion and an actuation portion.
- Track 4 is pivotally mounted about a pivot at 12.
- a first link 9 is pivotally mounted at one end about a pivot 150 on the valve actuator 10.
- the link 9 is pivotally mounted at its other end about a pivot 151.
- a second link 154 is pivotally mounted at one end about the pivot 151.
- the link 154 is pivotally mounted at its other end to a pivot 156.
- a third link 152 is pivotally mounted at one end about the pivot 151. At the other end of the link 152 is mounted a drive pin 31-32. the drive pin 31-32 engaging in the track 4. The separation between the drive pin 31-32 and the pivot 151 is equal to the radius of the lost motion portion of the track 4, and when the valve 11 is dosed, the pivot 151 is located at 12 such that the drive pin 31-32 will move freely around the lost motion portion of the track 4.
- a crankshaft 157 has a crank 158 thereon; the crank 158, via a fourth link 155, displaces the drive pin 31-32 along the track 4.
- crankshaft 157 which may be driven in suitable manner from the engine, will thus cause the linkage 155, 152 to oscillate causing drive pin 31-32 to reciprocate along the track 4. While the pin 31-32 engages the lost motion portion of track 4, the valve will remain closed. However, when the pin engages the actuation portion of the track 4, causes the linkage 154, 9 to oscillate causing valve 11 to open positively and to close positively.
- the opening and closing point of the valve 11 will correspond to when the drive pin 31-32 will pass from the lost motion portion of track 4 to the actuation portion of track 4 and from the actuation portion of the track 4 back to the lost motion portion of track 4.
- the angular displacement of the track 4 about 12 changes the opening and closing point of the valve and provides variable valve duration from a maximum to even zero if desirable.
- the angular displacement of the pivot 156 about 12 changes the valve lift and provides variable valve lift from a maximum to even zero, if desirable.
- the system is fully variable, i.e. after selecting the desirable valve duration by proper angular displacement of the track 4 about 12, the angular displacement of the pivot 156 about 12 changes continuously the valve lift without affecting the valve duration i.e. the system can change independently the valve lift and the valve duration.
- the necessarily heavy track 4 moves only when a different valve duration is desirable. This way the track 4, which is the heaviest part of the mechanism, stays substantially immovable during an engine cycle.
- the mechanism does not involve heavy parts, like track 4, that move or reciprocate at valve revs.
- the valve stem is free of bending loads.
- valve lash adjustment is either mechanical or hydraulic, Fig 13 .
- a basic valve lift profile can be adjusted to a desirable form. Then, by proper angular displacement of the track 4 and of the pivot 156, the basic valve lift profile is modified to meet the instant needs of the engine. Every single point of the hatched area in Fig 20 is achievable providing a different mode of operation, and for every mode of operation the lash, the acceleration and the jerk of the valve can stay acceptably small.
- FIG. 2 A simplified version of the system is shown in Fig 2 .
- the pivot 156, the link 154, the link 9 and the pivot 150 have been removed.
- the pivot 151 is transferred at the position of the former pivot 150 on the valve actuator 10.
- the angular displacement of the track 4 changes the valve duration and the valve lift from a maximum to even zero, if desirable.
- This version cannot provide independent variability for the valve lift and the valve duration.
- the absence of the links 154 and 9 increases the thrust loads on valve actuator 10 and makes difficult the track geometry, in terms of drive pin acceleration and of surface loading.
- the system can easily be adapted to new cylinder head designs.
- the system can also be applied on used engines as a retrofit kit, for instance as shown at Fig 19 wherein a side cam engine is modified.
- valve actuator 10 can be replaced by a rocker arm pivotally mounted at one end about a constant pivot, holding properly at its other end the valve.
- pivot 150 is secured on the rocker arm.
- an actuation pin can be used to displace the drive pin 31-32 along the track 4, like a linearly reciprocating pin or a pin reciprocating along an arc in synchronization to the engine etc.
- the track 4 can be replaced by a control surface 51, while a spring restores the valve to the valve seat, to provide a fully variable, but not desmodromic, valve train, like the one in Fig 15 .
- a pair of rollers 3 and 5, Figs 17 and 18 can replace the linkage 52, the first roller 3 rolling along a first control surface 7 that replaces the linkage 154, the second rollor 5 rolling along a second control surface 8 that replaces the track 4, while a cranshaft 1 wich a rotating control cam 2 can replace the crankshaft and the crank.
- the control cam 2 displaces the roller 5 along the control surface 8
- the roller 5 displaces the roller 3 along the control surface 7, so that the valve opens under the action of the control cam 2 and closes ur der the action of a restoring valve spring 6.
- the valve lift and the valve duration are continuously and independently variable.
- Figs 15 to 18 show the progressive degradation of the desmodromic mechanism of Fig 1 to a fully variable, but not desmodromic, valve actuation mechanism like the one described in US11/759,392 patent application.
- valve actuator 10 and the link 9 can be replaced by a rocker arm having a roller thereon, the latter roller being displaced by the roller 3.
Abstract
Description
- The closest prior art is the
US 6,892,684 patent. Instead of actuating the central swivel joint by a cam lobe, in the present invention the swivel joint is actuated positively in both directions by a link having a drive pin mounted at one end, the drive pin being engaged in a track to reciprocate therein. The resulting valve mechanism is rid of restoring springs of any kind, it operates reliably at racing revs because it is rid of heavy fast moving parts like the track, and it is fully variable: it can change continuously and independently the valve duration arid the valve lift from a maximum value to even zero, i.e. it can better approach the ideal valve lift profile for the instant operational conditions of the engine in terms of revs, load, air temperature coolant temperature, fuel quality, driving mode, altitude etc, i.e. it can optimize the operation and the thermal efficiency along a wider rev and load range. - Desmodromic variable valve actuation (VVA) is described in
US4,898,130 andUS35,016,581 US6,053,134 (Linebarger), inPCT/US2006/026429 (Decuir), inPCT/AU1998/000090 -
Fig 1 shows a preferred embodiment. -
Fig 2 shows a simplified Lost Motion version. This embodiment does not correspond to embodiments in accordance with this invention. -
Fig 3 shows, from two different points of view, a desmodromic fully variable valve actuation mechanism applied on a pair of valves. -
Figs 4 to 10 show the mechanism ofFig 3 after the removal of some parts to reveal the inner parts. -
Fig 11 shows some details of the mechanism ofFig 3 . -
Fig 12 shows another embodiment. This embodiment does not correspond to embodiments in accordance with this invention. -
Fig 13 shows at top a mechanical valve lash adjuster and at bottom a hydraulic valve lash adjuster. -
Fig 14 shows the mechanism ofFig 1 simplified. -
Figs 15 to 18 show obvious modifications of the basic mechanism ofFig 1 . These embodiments do not correspond to embodiments in accordance with this invention. -
Fig 19 shows the application of the valve mechanism in a Vee engine. -
Fig 20 shows the variability of the various valve trains in a lift-duration plot. -
Fig 21 shows the basic parts of a prototype cylinder head exhibited at international Engine Expo 2008, May 6 to 8, Stuttgart, Germany, details at www.pattakon.com -
FIG. 1 shows, in cross-section, a cylinder head with aninlet valve 11 slidably located in a valve guide. Thevalve 11 comprises a valve stem and a valve head, the latter being arranged to engage against a valve seat to close a port. Avalve actuator 10 is slidably fitted in aguide 101. Means, likenut 112,lash adjustment washer 114 andelastic washer 113 are also provided to accommodate the valve lash adjustment and the thermal expansion and to assure the sealing of the valve against its seat when the valve is closed. - A
track 4 is provided having a lost motion portion and an actuation portion.Track 4 is pivotally mounted about a pivot at 12. Afirst link 9 is pivotally mounted at one end about apivot 150 on thevalve actuator 10. Thelink 9 is pivotally mounted at its other end about apivot 151. - A
second link 154 is pivotally mounted at one end about thepivot 151. Thelink 154 is pivotally mounted at its other end to apivot 156. - A
third link 152 is pivotally mounted at one end about thepivot 151. At the other end of thelink 152 is mounted a drive pin 31-32. the drive pin 31-32 engaging in thetrack 4. The separation between the drive pin 31-32 and thepivot 151 is equal to the radius of the lost motion portion of thetrack 4, and when thevalve 11 is dosed, thepivot 151 is located at 12 such that the drive pin 31-32 will move freely around the lost motion portion of thetrack 4. - A
crankshaft 157 has acrank 158 thereon; thecrank 158, via afourth link 155, displaces the drive pin 31-32 along thetrack 4. - Rotation of the
crankshaft 157, which may be driven in suitable manner from the engine, will thus cause thelinkage track 4. While the pin 31-32 engages the lost motion portion oftrack 4, the valve will remain closed. However, when the pin engages the actuation portion of thetrack 4, causes thelinkage valve 11 to open positively and to close positively. - The opening and closing point of the
valve 11 will correspond to when the drive pin 31-32 will pass from the lost motion portion oftrack 4 to the actuation portion oftrack 4 and from the actuation portion of thetrack 4 back to the lost motion portion oftrack 4. The angular displacement of thetrack 4 about 12 changes the opening and closing point of the valve and provides variable valve duration from a maximum to even zero if desirable. - The angular displacement of the
pivot 156 about 12 changes the valve lift and provides variable valve lift from a maximum to even zero, if desirable. - This way the system is fully variable, i.e. after selecting the desirable valve duration by proper angular displacement of the
track 4 about 12, the angular displacement of thepivot 156 about 12 changes continuously the valve lift without affecting the valve duration i.e. the system can change independently the valve lift and the valve duration. - The necessarily
heavy track 4 moves only when a different valve duration is desirable. This way thetrack 4, which is the heaviest part of the mechanism, stays substantially immovable during an engine cycle. - To achieve reliable, low friction, high accuracy operation of the valve train at high revs, the mechanism does not involve heavy parts, like
track 4, that move or reciprocate at valve revs. - The valve stem is free of bending loads.
- The valve lash adjustment is either mechanical or hydraulic,
Fig 13 . - Keeping the rest mechanism the same and changing only the geometry of the
track 4, ccnsisting of theabutment surfaces track 4 and of thepivot 156, the basic valve lift profile is modified to meet the instant needs of the engine. Every single point of the hatched area inFig 20 is achievable providing a different mode of operation, and for every mode of operation the lash, the acceleration and the jerk of the valve can stay acceptably small. - Keeping both, the
track 4 and thepivot 156, immovable, the system degrades down to a single mode desmodromic valve train, represented by a point like C inFig 20 plot. - Keeping the
track 4 immovable and simply displacing angularly thepivot 156 about 12. the proposed system degrades down to a constant duration continuously variable lift va ve train, represented by a line like CDVVA inFig 20 plot, similar to the closest prior art. - Keeping the
pivot 156 immovable and simply displacing angularly thetrack 4 about 12 the proposed system degrades down to a lost motion continuously variable lift and duration valve train, represented by a curve like LMVVA infig 20 lot, similar to BMWs valvetronic. - A simplified version of the system is shown in
Fig 2 . Thepivot 156, thelink 154, thelink 9 and thepivot 150 have been removed. Thepivot 151 is transferred at the position of theformer pivot 150 on thevalve actuator 10. The angular displacement of thetrack 4 changes the valve duration and the valve lift from a maximum to even zero, if desirable. This version cannot provide independent variability for the valve lift and the valve duration. The absence of thelinks valve actuator 10 and makes difficult the track geometry, in terms of drive pin acceleration and of surface loading. - The system can easily be adapted to new cylinder head designs.
- The system can also be applied on used engines as a retrofit kit, for instance as shown at
Fig 19 wherein a side cam engine is modified. - For instance, the
valve actuator 10 can be replaced by a rocker arm pivotally mounted at one end about a constant pivot, holding properly at its other end the valve. In such a case thepivot 150 is secured on the rocker arm. - For instance, instead of the rotating
crank 158, an actuation pin can be used to displace the drive pin 31-32 along thetrack 4, like a linearly reciprocating pin or a pin reciprocating along an arc in synchronization to the engine etc. - For instance, the
track 4 can be replaced by acontrol surface 51, while a spring restores the valve to the valve seat, to provide a fully variable, but not desmodromic, valve train, like the one inFig 15 . - For instance, a pair of rollers 3 and 5,
Figs 17 and18 , can replace thelinkage 52, the first roller 3 rolling along afirst control surface 7 that replaces thelinkage 154, the second rollor 5 rolling along a second control surface 8 that replaces thetrack 4, while acranshaft 1 wich arotating control cam 2 can replace the crankshaft and the crank. Thecontrol cam 2 displaces the roller 5 along the control surface 8, the roller 5 displaces the roller 3 along thecontrol surface 7, so that the valve opens under the action of thecontrol cam 2 and closes ur der the action of a restoring valve spring 6. Depending on the angular displacement of thecontrol surfaces 7 and 8, the valve lift and the valve duration are continuously and independently variable.Figs 15 to 18 show the progressive degradation of the desmodromic mechanism ofFig 1 to a fully variable, but not desmodromic, valve actuation mechanism like the one described inUS11/759,392 valve actuator 10 and thelink 9 can be replaced by a rocker arm having a roller thereon, the latter roller being displaced by the roller 3. - Although the invention has been described and illustrated in detail, the spirit and scope of the present invention are to be limited only by the terms of the appended claims.
Claims (7)
- A desmodromic valve mechanism comprising at least:a valve (11);a valve actuator (10), said valve actuator (10) being attached adjacent to the valve (11);a first link (9), said first link (9) being pivotally mounted at one end about a pivot (150) on said valve actuator (10), said link (9) being pivotally mounted at its other end about a pivot (151);a second link (154), said second link (154) being pivotally mounted to a control pivot (156);a third link (152), said third link (152) being pivotally mounted at one end about said pivot (151),characterized in that it comprisesa track (4);said second link (154) being pivotally mounted at one end about said pivot (151), said second link (154) being pivotally mounted at its other end to the control pivot (156);a drive pin (31-32),said drive pin (31-32) being engaged in said track (4);said drive pin (31-32) being mounted at the other end of said third link (152);an actuation pin (158), said actuation pin (158), via a fourth link (155), displaces said drive pin (31-32) along said track (4), said track (4) comprising a lost motion portion and an actuation portion,so that motion of the actuation pin will cause the linkage to oscillate and the drive pin to perform a reciprocating motion along the track, so that engagement of the lost motion portion of the track by the drive pin will cause the valve to stay closed, so that engagement of the actuation portion of the track by the drive pin will cause the valve to move opening and closing, so that the valve mechanism is rid of inertia loads from moving tracks offering higher engine speed limit.
- A desmodromic valve mechanism according claim 1 wherein the control pivot (156) is angularly displaceable about a center (12) to control the valve lift of the valve (11).
- A desmodromic valve mechanism according claim 1 wherein the track (4) is angularly displaceable about a center (12) to control the valve duration of the valve (11).
- A desmodromic valve mechanism according claim 1 wherein the control pivot (156) is angularly displaceable about a center (12) and the track (4) is angularly displaceable about the same center (12) to provide independently variable lift and duration to the valve (11).
- A desmodromic valve mechanism according claim 1 wherein the valve actuator (10) is slidably fitted in a guide (101).
- A desmodromic valve mechanism according claim 1 wherein the valve actuator (10) comprises lash adjustment means (112, 114) and elastic means (113) to compensate for heat expansion and to assist the sealing between the valve and the seat of the valve, when the valve is closed.
- A desmodromic valve mechanism according claim 1 wherein the valve actuator (10) is a valve lever pivotally mounted at one end and attached adjacent at the other end to the stem of the valve (11).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/759,392 US7765965B2 (en) | 2007-06-07 | 2007-06-07 | Fully variable valve actuation |
US11/764,970 US20080314342A1 (en) | 2007-06-19 | 2007-06-19 | Desmodromic variable valve actuation |
PCT/IB2008/052228 WO2008149316A2 (en) | 2007-06-07 | 2008-06-06 | Desmodromic variable valve actuation |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2198129A2 EP2198129A2 (en) | 2010-06-23 |
EP2198129B1 true EP2198129B1 (en) | 2011-05-25 |
Family
ID=39791740
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08763225A Not-in-force EP2198129B1 (en) | 2007-06-07 | 2008-06-06 | Desmodromic variable valve actuation |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2198129B1 (en) |
AT (1) | ATE510999T1 (en) |
WO (1) | WO2008149316A2 (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB201307317D0 (en) | 2013-04-23 | 2013-05-29 | Camcon Auto Ltd | Valve System and Methods of Operation Thereof |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR557079A (en) * | 1922-01-25 | 1923-08-02 | Combustion engine | |
DE3022188A1 (en) * | 1980-06-13 | 1981-12-24 | Teodoro 4300 Essen Holtmann | VALVE CONTROL DEVICE OF AN INTERNAL COMBUSTION ENGINE |
GB8920361D0 (en) * | 1989-09-08 | 1989-10-25 | Jaguar Cars | Valve mechanisms |
ES2120346B1 (en) * | 1995-11-10 | 1999-05-16 | Campo Garraza Pedro Jose | ALTERNATIVE LINEAR DRIVE MECHANICAL DEVICE. |
DE10100173A1 (en) * | 2001-01-04 | 2002-07-11 | Fev Motorentech Gmbh | Fully variable mechanical valve train for a piston internal combustion engine |
DE10155007A1 (en) * | 2001-11-06 | 2003-05-15 | Herbert Naumann | Valve stroke |
-
2008
- 2008-06-06 AT AT08763225T patent/ATE510999T1/en not_active IP Right Cessation
- 2008-06-06 EP EP08763225A patent/EP2198129B1/en not_active Not-in-force
- 2008-06-06 WO PCT/IB2008/052228 patent/WO2008149316A2/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
ATE510999T1 (en) | 2011-06-15 |
WO2008149316A2 (en) | 2008-12-11 |
EP2198129A2 (en) | 2010-06-23 |
WO2008149316A3 (en) | 2009-03-12 |
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