EP0548294B1 - Method of operating a valve system with recuperation - Google Patents
Method of operating a valve system with recuperation Download PDFInfo
- Publication number
- EP0548294B1 EP0548294B1 EP92900062A EP92900062A EP0548294B1 EP 0548294 B1 EP0548294 B1 EP 0548294B1 EP 92900062 A EP92900062 A EP 92900062A EP 92900062 A EP92900062 A EP 92900062A EP 0548294 B1 EP0548294 B1 EP 0548294B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure fluid
- high pressure
- plunger surface
- towards
- 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.)
- Expired - Lifetime
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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
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- 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.
- 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 valve systems will be comparable to mechanical valve systems.
- EP-A-0520633, which belongs to the prior art according to Art. 54(3) EPC discloses a method of operating a valve system having a valve with a plunger surface and being displaceable between first and second positions, a first means for biasing the valve towards the first position, a source of relatively high pressure fluid, and a source of relatively low pressure fluid, the method comprising causing the valve to be displaced from the second position towards the first position by, during a first portion of the displacement, not communicating the high pressure fluid to the plunger surface and communicating the low pressure fluid to the plunger surface whereby the first means urges the valve towards the first position; during a second portion of the displacement of the valve from the second position towards the first position, prior to the valve reaching the first position, ceasing communication of the plunger surface with the low pressure fluid and communicating high pressure fluid to the plunger surface; whereby the momentum of the valve carries the valve towards the first position and pumps the high pressure fluid in communication with the plunger surface back to the high pressure fluid source. EP-A-0520633 does not disclose that the communication between the plunger surface and the high and low pressure fluids is controlled by a single valve.
- EP-A-0520633 discloses a valve system having a valve with a plunger surface and being displaceable between first and second positions, a first means for biasing the valve towards the first position, a source of relatively high pressure fluid, and a source of relatively low pressure fluid, means for causing the valve to be displaced from the second position towards the first position by, during a first portion of the displacement, not communicating the high pressure fluid to the plunger surface and communicating the low pressure fluid to the plunger surface whereby the first means urges the valve towards the first position; and means for ceasing communication of the plunger surface with the low pressure fluid and communicating high pressure fluid to the plunger surface during a second portion of the displacement of the valve from the second position towards the first position; prior to the valve reaching the first position, whereby the momentum of the valve carries the valve towards the first position and pumps the high pressure fluid in communication with the plunger surface back to the high pressure fluid source. EP-A-0520633 does not disclose that there is a single valve for controlling the communication between the plunger surface and the high and low pressure fluids.
- JP-A-60085209 discloses a method of operating a valve system, according to the preamble of claim 1, as well as a valve system according to the preamble of claim 5, for each of the countries designated.
- The object of the invention is achieved by a method and a system according to claims 1 and 5 for DE, GB, FR, as well as for BE.
- 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.
- In the accompanying 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 "dsv" as a function of time "t". The top graph shows engine valve displacement "dev" as a function of time "t".
- 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), aplunger 14 integrally formed with or separately positioned adjacent to eachengine valve 12 having aplunger surface 16, first means, preferably a pair ofhelical compression springs 18, for biasing eachengine valve 12 towards its first position, asource 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 arail 25 between one of the lowpressure fluid source 20 or the high pressure fluid source 22 and theplunger surface 16. The spool valve 24 is biased to a first position (shown) by ahelical compression spring 26 and moved against the force of thespring 26 to a second position (not shown) to the right of the first position by an actuator. In this embodiment, the actuator is apiezoelectric motor 28. Adjacent the piezoelectric motor is a relativelylarge diameter piston 30, and spring biased array which is in hydraulic communication with a relativelysmall 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 acylinder head 34. - The
plunger 16 is reciprocally guided in abore 36 of avalve 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 therail 25 and at theplunger 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.
- 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 A₁ 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 t₁ a voltage VH is sent to thepiezoelectric motor 28. Thepiezoelectric motor 28 expands, thus driving thelarge piston 30, which through hydraulic communication drives thesmall piston 32, which in turn drives the spool valve 24 from its first position PL to its second position PH. - Movement of the spool valve 24 from the first position PL to the second position PH closes off communication of the
low pressure source 20 with theplunger surface 16 and opens communication of the high pressure source 22 with theplunger surface 16. The high pressure fluid is great enough to cause theengine valve 12 to open against the force of thecompression springs 18. Communication of the high pressure source 22 with theplunger surface 16 is maintained during a first portion of displacement of theengine valve 12 from A₁ to A₂ until sufficient momentum is built up in theengine valve 12 so that it will coast to full open. - At engine valve displacement A₂, corresponding to t₂, the voltage is removed from the
piezoelectric motor 28, resulting in the spool valve 24 returning under the force of thesprings 26 from its second position PH to its first position PL cutting off communication of the high pressure fluid with theplunger surface 16 and again communicating low pressure fluid with theplunger surface 16. - From A₂, the momentum in the
engine valve 12 is able to carry it to full open A₃. The increasing volume of therail 25, created by theplunger 14 moving down with theengine 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 theengine valve 12 can be reduced by about 10 to 20%, depending upon cylinder pressure and other factors. Analytically, from A₁ to A₃, potential energy in the high pressure fluid is converted into kinetic energy of the movingengine valve 12 and potential energy in thecompression 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 thecompression springs 18. Maximum designed displacement is reached when the hydraulic pressure and the force of thecompression spring 18 are in equilibrium or when theplunger 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, theengine valve 12 can overshoot its equilibrium position due to the increasing momentum of theengine valve 12 which can damage thesprings 18 and cause theengine valve 12 to oscillate. Even with a stop, if theplunger 14 hits the stop at full speed, it can cause wear, breakage, and oscillation. - At t₃, corresponding to A₃ of the
engine valve 12, thepiezoelectric motor 28 is again energized, again forcing the spool valve 24 to its second position PH, thus switching the fluid in communication with theplunger surface 16 from low pressure to high pressure. In this manner, theengine valve 12 is able to be maintained open against the force of thecompression springs 18. Between t₃ and t₄, the velocity of the engine valve is zero. Theengine valve 12 is held open in this manner until the appropriate time t₄ in the engine cycle for it to close. - At t₄, the voltage is removed from the
piezoelectric motor 28 allowing the spool valve 24 to return from its second position PH to its first position PL thus switching the fluid in communication with theplunger surface 16 from high pressure to low pressure, thereby allowing theengine valve 12 to begin its closing stroke. At this stage, the potential energy of thecompression springs 18 is turned into kinetic energy in the movingengine valve 12. The lowpressure fluid supply 20 is maintained in communication with theplunger surface 16 until there is sufficient momentum to close theengine 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 PL to its second position PH, thus switching the fluid in communication with theplunger surface 16 from low pressure to high pressure. Because enough momentum is in theengine valve 12 to carry it to its closed position A₆ against the force of the high pressure fluid, theplunger 14 now acts like a fluid pump by returning fluid under pressure to the high pressure source 22 as the valve moves from A₅ to A₆. This is the hydraulic energy recuperation portion of the cycle. Analytically, the kinetic energy of theengine 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 theengine 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 theengine valve 12 at A₆ is zero since theengine 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 PH to its first position PL, thus switching the fluid in communication with theplunger surface 16 from high pressure to low pressure, otherwise theengine 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 theengine 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 theengine valve 12 so that hydraulic power consumption is minimized. Second, the displacement of theengine valve 12 in the opening direction is controlled so that the theengine valve 12 does not overshoot its equilibrium position at full open. Third, the displacement of theengine valve 12 in the closing direction is controlled so that valve seating velocity is minimized. Fourth, the system is capable of opening and closing theengine 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 theengine 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.
Claims (8)
- A method of operating a valve system (10) having a valve (12) with a plunger surface (16) and being displaceable between first and second positions, a first means (18) for biasing the valve (12) towards the first position, a source of relatively high pressure fluid (22), and a source of relatively low pressure fluid (20), the method comprising causing the valve (12) to be displaced from the second position towards the first position by, during a first portion of the displacement, not communicating the high pressure fluid (22) to the plunger surface (16) and communicating the low pressure fluid (20) to the plunger surface (16) whereby the first means (18) urges the valve (12) towards the first position; characterised by, during a second portion of the displacement of the valve (12) from the second position towards the first position, prior to the valve (12) reaching the first position, ceasing communication of the plunger surface with the low pressure fluid (20) and communicating high pressure fluid (22) to the plunger surface (16); whereby the momentum of the valve (12) carries the valve (12) towards the first position and pumps the high pressure fluid (22) in communication with the plunger surface (16) back to the high pressure fluid source (22).
- A method according to claim 1, preceded or succeeded by the steps of communicating high pressure fluid (22) to the plunger surface (16) of the valve (12) while the valve (12) is at its first position; temporarily maintaining fluid communication between the high pressure fluid (22) and the plunger surface during a first portion of displacement of the valve (12) from its first position towards its second position and ceasing communication of the high pressure fluid (22) with the plunger surface (16) during a second portion of displacement of the valve (12) from its first position towards its second position, prior to reaching its second position, whereupon the valve continues moving towards its second position.
- A method according to claim 2, wherein when the valve (12) reaches the second position the high pressure fluid (22) is again communicated with the plunger surface (16) and when the valve is to be returned to the first position, communication of the high pressure fluid (22) with the plunger surface (16) is ceased.
- A method according to claim 2 or claim 3, wherein when the communication of the high pressure fluid (22) with the plunger surface (16) is ceased, during the displacement of the valve from its first position towards its second position, the plunger surface (16) is put in communication with the low pressure fluid (20).
- A valve system (10) having a valve (12) with a plunger surface (16) and being displaceable between first and second positions, a first means (18) for biasing the valve (12) towards the first position, a source of relatively high pressure fluid (22), and a source of relatively low pressure fluid (20), means for causing the valve (12) to be displaced from the second position towards the first position by, during a first portion of the displacement, not communicating the high pressure fluid (22) to the plunger surface (16) and communicating the low pressure fluid (20) to the plunger surface (16) whereby the first means (18) urges the valve (12) towards the first position; characterised by means for ceasing communication of the plunger surface with the low pressure fluid (20) and communicating high pressure fluid (22) to the plunger surface (16) during a second portion of the displacement of the valve (12) from the second position towards the first position, prior to the valve (12) reaching the first position; whereby the momentum of the valve (12) carries the valve (12) towards the first position and pumps the high pressure fluid (22) in communication with the plunger surface (16) back to the high pressure fluid source (22).
- A system according to claim 1, further comprising means for communicating high pressure fluid (22) to the plunger surface (16) of the valve (12) while the valve (12) is at its first position; and means for temporarily maintaining fluid communication between the high pressure fluid (22) and the plunger surface during a first portion of displacement of the valve (12) from its first position towards its second position and ceasing communication of the high pressure fluid (22) with the plunger surface (16) during a second portion of displacement of the valve (12) from its first position towards its second position, prior to reaching its second position, whereupon the valve continues moving towards its second position.
- A system according to claim 6, further comprising means for communicating the high pressure fluid (22) with the plunger surface (16) when the valve (12) reaches the second position, and ceasing communication of the high pressure fluid (22) with the plunger surface (16) when the valve is to be returned to the first position.
- A system according to claim 6 or claim 7, further comprising means for communicating the plunger surface (16) with the low pressure fluid (20) when the communication of the high pressure fluid (22) with the plunger surface (16) is ceased, during the displacement of the valve from its first position towards it second position.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US72913891A | 1991-07-12 | 1991-07-12 | |
US729138 | 1991-07-12 | ||
PCT/US1991/007451 WO1993001399A1 (en) | 1991-07-12 | 1991-10-10 | Recuperative engine valve system and method of operation |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0548294A1 EP0548294A1 (en) | 1993-06-30 |
EP0548294B1 true 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 |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0328193A1 (en) * | 1988-02-08 | 1989-08-16 | Magnavox Electronic Systems Company | Pneumatically powered valve actuator |
Family Cites Families (1)
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 |
-
1991
- 1991-10-10 EP EP92900062A patent/EP0548294B1/en not_active Expired - Lifetime
- 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
- 1991-10-10 DE DE69114509T patent/DE69114509T2/en not_active Expired - Fee Related
- 1991-10-10 AU AU90172/91A patent/AU9017291A/en not_active Abandoned
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0328193A1 (en) * | 1988-02-08 | 1989-08-16 | Magnavox Electronic Systems Company | Pneumatically powered valve actuator |
Also Published As
Publication number | Publication date |
---|---|
WO1993001399A1 (en) | 1993-01-21 |
EP0548294A1 (en) | 1993-06-30 |
JPH06501081A (en) | 1994-01-27 |
DE69114509D1 (en) | 1995-12-14 |
DE69114509T2 (en) | 1996-07-04 |
AU9017291A (en) | 1993-02-11 |
JP3121011B2 (en) | 2000-12-25 |
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