EP0548294A1 - Recuperative engine valve system and method of operation. - Google Patents
Recuperative engine valve system and method of operation.Info
- Publication number
- EP0548294A1 EP0548294A1 EP92900062A EP92900062A EP0548294A1 EP 0548294 A1 EP0548294 A1 EP 0548294A1 EP 92900062 A EP92900062 A EP 92900062A EP 92900062 A EP92900062 A EP 92900062A EP 0548294 A1 EP0548294 A1 EP 0548294A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure fluid
- high pressure
- fluid
- plunger surface
- 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.)
- Granted
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.A recovery engine valve system (10) for an internal combustion engine. The system includes an engine valve (12) having a piston surface (16), a first device (20) for urging the engine valve (12) to close, a source of fluid (22) including the pressure is relatively low, a source of fluid (24) whose pressure is relatively high, and a second device (28) selectively serving to circulate the fluid between the piston surface (16) and one of the two sources of fluid ( 22 and 24) at low and high pressures. The duration of selective circulation of the low pressure fluid and the high pressure fluid to the piston surface (16) during movement of the valve is controlled so as to save and recover energy.
Description
Description
RECUPERATIVE ENGINE VALVE SYSTEM AND METHOD OF OPERATION
Technical Field
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.
Background Art
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.
One disadvantage typically associated with hydraulic systems is the high amount of hydraulic energy necessary to quickly actuate an engine valve. High energy consumption is particularly evident when the engine valve is an exhaust poppet valve that must open against relatively high gas pressure developed in an engine combustion chamber during the compression and combustion phases. This power consumption can be seventy-five percent higher than the power required to actuate typical mechanical engine valves.
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.
Disclosure of the Invention In one aspect of the present invention, 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, is disclosed. 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.
In another aspect of the present invention, a method of operating a hydraulically-actuated valve system is disclosed. The method 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.
Brief Description of the Drawings
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".
Best Mode for Carrying Out the Invention
Referring to 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. 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. In this embodiment, 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.
Industrial Applicability
For clarity, 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 PL in the middle graph of Fig. 2. To begin the valve opening sequence, at t- a voltage V„ 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 PL to its second position P„ri. Movement of the spool valve 24 from the first position Pτ _J to the second position l?„Jti closes off communication of the low pressure source 20 with the plunger surface 16 and opens communication of the high pressure source 22 with the plunger surface 16. 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.
At engine valve displacement A_, corresponding to t,, the voltage is removed from the piezoelectric motor 28, resulting in the spool valve 24 returning under the force of the springs 26 from
its second position P„ to its first position P_ cutting off communication of the high pressure fluid with the plunger surface 16 and again communicating low pressure fluid with the plunger surface 16. From A_, the momentum in the engine valve 12 is able to carry it to full open A_. The increasing volume of the rail 25, created by the plunger 14 moving down with the engine valve 12, is filled with low pressure rather than high pressure fluid, thereby conserving hydraulic energy during the coasting period. In this manner, the hydraulic power required to open the engine valve 12 can be reduced by about 10 to 20%, depending upon cylinder pressure and other factors. Analytically, from A. to A3, potential energy in the high pressure fluid is converted into kinetic energy of the moving engine valve 12 and potential energy in the compression springs 18.
At maximum displacement of the engine valve A3 (full open) , the kinetic energy of the engine valve 12 has been transformed into potential energy stored in the compression springs 18. Maximum designed displacement is reached when the hydraulic pressure and the force of the compression spring 18 are in equilibrium or when the plunger 14 contacts a physical stop. In the absence of a plunger stop, if the fluid supply is not switched to low pressure before full open, the engine valve 12 can overshoot its equilibrium position due to the increasing momentum of the engine valve 12 which can damage the springs 18 and cause the engine valve 12 to oscillate. Even with a stop, if the plunger 14 hits the stop at full speed, it can cause wear, breakage, and oscillation.
At t_, corresponding to A_ of the engine valve 12, the piezoelectric motor 28 is again
energized, again forcing the spool valve 24 to its second position P„, 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.
At t., the voltage is removed from the piezoelectric motor 28 allowing the spool valve 24 to return from its second position P„ to its first position PL 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. At this stage, 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.
At engine valve displacement A5, corresponding to t5, the piezoelectric motor 28 is again energized, moving the spool valve 24 from its first position P Jτ_ to its second position P„ii, 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 Ag. 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.
About 30% to 50% of the hydraulic energy originally used to open the engine valve 12 can be recuperated during this phase. Pressure drops across the spool valve 24 and friction losses in the system limit the recuperation from being 100%. Of course, the velocity of the engine valve 12 at Kco is zero since the engine valve 12 has again seated.
As soon as the valve seats, the piezoelectric motor 28 is deenergized and the spool valve 24 moves from its second position P„ _ι 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.
Note that the system described herein could be reversed as a matter of design choice such that the engine valve 12 is biased towards it open position and high pressure fluid is used to urge the engine valve 12 towards its closed position.
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.
While the present invention has been shown and explained as used with a poppet engine valve 12 of a combustion chamber of an engine, it is to be understood that the present invention is applicable to any hydraulically actuated valve that can benefit from its advantages.
Other aspects, objects, and advantages of this invention can be obtained from a study of the drawings, the disclosure, and the appended claims.
Claims
1. A valve system (10) comprising: a valve (12) having a plunger surface (16) , said valve (12) being displaceable between a first position and a second position; first means (20) for biasing said valve towards said first position; a source of relatively low pressure fluid (22) ; a source of relatively high pressure fluid (24) ; and second means (28) for selectively communicating fluid between said plunger surface (16) and said low pressure fluid source (22) and said high pressure fluid source (24) ; said plunger surface (16) being operable to urge said valve (12) towards said second position when said plunger surface (16) is in fluid communication with said high pressure fluid source (24) ; and said plunger surface (16) being operable to return said fluid under pressure to said high pressure fluid source (24) when said valve (12) moves in the direction from said second position towards said first position.
2. The valve system (.10) of claim 1, said second means (28) being displaceable between a first position at which only one of said low pressure fluid (22) and said high pressure fluid (24) is in fluid communication with said plunger surface (16) and a second position at which only the other of said low pressure fluid (22) and said high pressure fluid (24) is in fluid communication with said plunger surface (16) .
3. The valve system (10) of claim 3, said fluid pressure of said high pressure fluid (24) being at least about 1500 psi.
4. The valve system (10) of claim 3, said fluid pressure of said low pressure fluid (22) being less than about 400 psi.
5. A method of operating a valve system (10) , comprising the steps of: communicating high pressure fluid (24) to a plunger surface (16) of a valve (12) while the valve (12) is at its first position; temporarily maintaining fluid communication between the high pressure fluid (24) and the plunger surface (16) during a first portion of displacement of the valve (12) from its first position towards its second position; and ceasing communication of said high pressure fluid (24) with said plunger surface (16) during a second portion of displacement of the valve (12) prior to reaching its second position whereby momentum of the valve (12) carries the valve (12) towards its second position.
6. The method of claim 5, wherein when said valve (12) reaches said second position said high pressure fluid (24) is again communicated with said plunger surface (16) .
7. The method of claim 6, wherein when said valve (12) is to be returned to said first position, communication of said high pressure fluid (24) with said plunger surface (16) is ceased.
8. The method of claim 7, wherein non-communication between said high pressure fluid (24) and said plunger surface (16) is maintained during a first portion of displacement of said valve (12) from said second position towards said first position and prior to said valve (12) reaching said first position, said high pressure fluid (24) is communicated with said plunger surface (16) during a second portion of the displacement of said valve (12) from said second position towards said first position.
9. The method of claim 6, wherein when said communication of said high pressure fluid (24) with said plunger surface (16) is ceased, said plunger surface (16) is put in communication with said low pressure fluid (22) .
10. A method of operating a valve system (10) having a valve (12) having a plunger surface (16) and being displaceable between first and second positions, a first means (20) for biasing said valve (12) towards said first position, a source of relatively high pressure fluid (24) , and a source of relatively low pressure fluid (22) , comprising the steps of: at said second position of said valve (12) , not communicating said high pressure fluid (24) to said plunger surface (16) ; said first means (20) urging said valve (12) towards said first position; prior to said valve (12) reaching said first position, communicating high pressure fluid (24) to said plunger surface (16) ; and the momentum of said valve (12) carrying said valve (12) towards said valve's (12) first position and pumping said high pressure fluid (24) in communication with said plunger surface (16) back to said high pressure fluid source (24) .
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US72913891A | 1991-07-12 | 1991-07-12 | |
| PCT/US1991/007451 WO1993001399A1 (en) | 1991-07-12 | 1991-10-10 | Recuperative engine valve system and method of operation |
| US729138 | 2003-12-05 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0548294A1 true EP0548294A1 (en) | 1993-06-30 |
| EP0548294B1 EP0548294B1 (en) | 1995-11-08 |
Family
ID=24929747
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP92900062A Expired - Lifetime EP0548294B1 (en) | 1991-07-12 | 1991-10-10 | Method of operating a valve system with recuperation |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP0548294B1 (en) |
| JP (1) | JP3121011B2 (en) |
| AU (1) | AU9017291A (en) |
| DE (1) | DE69114509T2 (en) |
| WO (1) | WO1993001399A1 (en) |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5638781A (en) * | 1995-05-17 | 1997-06-17 | Sturman; Oded E. | Hydraulic actuator for an internal combustion engine |
| EP0767295B1 (en) * | 1995-10-03 | 2000-03-08 | Wärtsilä NSD Schweiz AG | Hydraulic valve |
| ITBO20000548A1 (en) | 2000-09-22 | 2002-03-22 | Magneti Marelli Spa | COMBUSTION ENGINE FOR MOTOR VEHICLES AND SIMILAR |
| DE10124869C2 (en) * | 2001-05-22 | 2003-06-26 | Caterpillar Motoren Gmbh & Co | Hydraulic control device for equivalent engine valves of a diesel engine |
| EP2063075A1 (en) * | 2007-11-23 | 2009-05-27 | EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt | Fluid actuated valve mechanism |
| EP3406866A1 (en) | 2017-05-22 | 2018-11-28 | EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt | Hydraulic drive for accelerating and braking components to be dynamically moved |
| EP3656990A1 (en) | 2018-11-22 | 2020-05-27 | EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt | Hydraulic drive for accelerating and braking components to be dynamically moved |
| WO2021121639A1 (en) | 2019-12-20 | 2021-06-24 | Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt | Hydraulic drive for accelerating and braking components that are to be moved dynamically |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2552492B1 (en) * | 1983-09-23 | 1988-01-15 | Alsacienne Constr Meca | ELECTRO-HYDRAULIC VALVE CONTROL UNIT FOR AN INTERNAL COMBUSTION ENGINE |
| US4899700A (en) * | 1988-02-08 | 1990-02-13 | Magnavox Government And Electronic Company | Pneumatically powered valve actuator |
-
1991
- 1991-10-10 AU AU90172/91A patent/AU9017291A/en not_active Abandoned
- 1991-10-10 EP EP92900062A patent/EP0548294B1/en not_active Expired - Lifetime
- 1991-10-10 DE DE69114509T patent/DE69114509T2/en not_active Expired - Fee Related
- 1991-10-10 JP JP04500684A patent/JP3121011B2/en not_active Expired - Fee Related
- 1991-10-10 WO PCT/US1991/007451 patent/WO1993001399A1/en active IP Right Grant
Non-Patent Citations (1)
| Title |
|---|
| See references of WO9301399A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| AU9017291A (en) | 1993-02-11 |
| WO1993001399A1 (en) | 1993-01-21 |
| DE69114509D1 (en) | 1995-12-14 |
| JPH06501081A (en) | 1994-01-27 |
| EP0548294B1 (en) | 1995-11-08 |
| JP3121011B2 (en) | 2000-12-25 |
| DE69114509T2 (en) | 1996-07-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5152260A (en) | Highly efficient pneumatically powered hydraulically latched actuator | |
| US6067946A (en) | Dual-pressure hydraulic valve-actuation system | |
| US4000756A (en) | High speed engine valve actuator | |
| KR101215988B1 (en) | variable valve actuator with a pneumatic booster | |
| US3926159A (en) | High speed engine valve actuator | |
| US5058538A (en) | Hydraulically propelled phneumatically returned valve actuator | |
| JPH1054322A (en) | Hydraulic operation type fuel injector having direct controlling needle valve | |
| JP3326219B2 (en) | Electrically controlled hydraulically driven valve actuator | |
| JP2004510907A (en) | Device for operating valve and method of controlling the device | |
| JP2645942B2 (en) | Method and apparatus for controlling supply and exhaust valves of an internal combustion engine | |
| EP0885349B1 (en) | Outwardly opening valve system for an engine | |
| EP0548294A1 (en) | Recuperative engine valve system and method of operation. | |
| JP2005528563A (en) | Pressure pulse generation method and pressure pulse generator | |
| JPH05106759A (en) | Spring driving hydraulic actuator | |
| JPH0719205A (en) | Asymmetric bistable pneumatically operated actuator mechanism | |
| JP4580937B2 (en) | System and method for preventing collision between piston and valve of non-freewheel internal combustion engine | |
| US5709178A (en) | Electronically controlled outwardly opening valve system for an engine | |
| US6474620B2 (en) | Method of controlling hydraulically actuated valves and engine using same | |
| EP1025345B1 (en) | Internal combustion engine with compressor function | |
| JPH07189633A (en) | Valiable valve system of internal combustion engine | |
| WO1997019260A1 (en) | Valve operating system | |
| AU714090B2 (en) | Valve operating system | |
| JPH07233718A (en) | Variable valve system for internal combustion engine | |
| JPH08200027A (en) | Engine brake apparatus | |
| JPH07189634A (en) | Variable valve system for internal combustion engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| 17P | Request for examination filed |
Effective date: 19930408 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): BE DE FR GB |
|
| 17Q | First examination report despatched |
Effective date: 19940531 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): BE DE FR GB |
|
| REF | Corresponds to: |
Ref document number: 69114509 Country of ref document: DE Date of ref document: 19951214 |
|
| ET | Fr: translation filed | ||
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed | ||
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20000913 Year of fee payment: 10 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20001012 Year of fee payment: 10 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20010926 Year of fee payment: 11 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20011031 |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
| BERE | Be: lapsed |
Owner name: CATERPILLAR INC. Effective date: 20011031 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20020628 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20021010 |
|
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20021010 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20031031 Year of fee payment: 13 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050503 |