EP1341992B1 - Vorrichtung zum betätigen der ventile und steuerungsverfahren dafür - Google Patents

Vorrichtung zum betätigen der ventile und steuerungsverfahren dafür Download PDF

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Publication number
EP1341992B1
EP1341992B1 EP01974436A EP01974436A EP1341992B1 EP 1341992 B1 EP1341992 B1 EP 1341992B1 EP 01974436 A EP01974436 A EP 01974436A EP 01974436 A EP01974436 A EP 01974436A EP 1341992 B1 EP1341992 B1 EP 1341992B1
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EP
European Patent Office
Prior art keywords
valve
pressure
chamber
actuation
source
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Expired - Lifetime
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EP01974436A
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English (en)
French (fr)
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EP1341992A1 (de
Inventor
Serge Masse
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Alpine Racing SAS
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Renault Sport SAS
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Publication of EP1341992A1 publication Critical patent/EP1341992A1/de
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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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L1/462—Valve return spring arrangements
    • F01L1/465—Pneumatic arrangements
    • 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 invention relates to a device for actuating the valves of a motor vehicle engine.
  • the invention relates more particularly to a device for actuating the valves of a motor vehicle engine, of the type in which each valve comprises a rod or tail which is integral with an actuator controlled by a control unit to cause the lifting and the return of the associated valve, of the type in which each actuator is in the form of a cylinder which comprises a cylinder inside which the tail of the associated valve is free to slide coaxially in a sealed manner, and inside which is arranged a movable piston, secured to the free end of the valve stem, which delimits in the cylinder two opposed upper and lower hydraulic pressure chambers which are each supplied with an incompressible fluid and in each of which is established alternatively a pressure of said fluid which is regulated by the control unit so that the pressure prevailing in a chambers alternately higher / lower than that prevailing in the other chamber, to alternately actuate the cylinder and the valve.
  • valve lift laws which are determined by the control unit according to the operating mode. rotation of the motor, so as to optimize the operation of said engine.
  • the "camless” actuators comprise actuators which are of the electromagnetic or hydraulic type.
  • An electromagnetic actuator essentially comprises two springs and a metal pallet moving between two coils.
  • the valve When the valve is closed, the upper spring is held compressed by the pallet which is attracted to the upper coil which is excited by an electric current. No excitation is created by the lower coil and the lower spring is at rest.
  • the paddle When the flow of current in the upper coil is interrupted, the paddle is released and causes the valve to open while compressing the lower spring.
  • the actuating device is said to be "oscillating" insofar as the potential energy of the upper spring is transferred to the pallet in the form of kinetic energy and then transferred back in the form of potential energy to the lower spring.
  • the valve is then kept open by establishing a flow of current in the lower coil.
  • the interruption of the current in the lower coil causes the closing of the valve and the recompression of the upper spring.
  • Actuating devices comprising electromagnetic actuators have the disadvantage of requiring a high electrical power to ensure their operation.
  • the only power that is consumed by the actuators of a motor vehicle "camless" can reach, for a four-cylinder engine and 16 valves, the value of 2 kiloWatts at maximum engine speed, while a conventional motor vehicle consumes the same power to ensure the full operation of its electrical accessories.
  • the supply voltage of the vehicle's electrical circuit which is conventionally 12 volts, must be increased to 42 volts to reduce the size of the generator.
  • the electromagnetic actuators are unsuitable for engines operating at high rotation speeds. Indeed, for such motors, the electromagnetic actuators do not allow to perform sufficient acceleration of moving parts beyond the usual speeds of the series engines.
  • this device does not effectively control the speed of the valve at the end of closing stroke, or at least it allows to control the speed of the valve at the cost of additional consumption of hydraulic energy .
  • Such a device therefore has the disadvantage of risking degrading the seat of said valve and generating noise if it closes on its seat with too high a speed, or the disadvantage of significantly puncture the power of the seat. engine.
  • US-A-5,572,961 discloses a similar device wherein the return of the valve is achieved by means of a spring.
  • a device is of the "oscillating" type described above and makes it possible to significantly reduce the consumption of hydraulic energy required for the actuation of the valve.
  • this device proves unsuited to high revolutions of the engine, and in particular so-called “valve malfunction" regimes for which the spring, resonating, may be subject to oscillations, uncontrollable, d high amplitude.
  • the invention proposes a hydraulic and oscillating device which is produced in the form of a "camless" hydropneumatic distribution system.
  • each hydraulic pressure chamber of the jack is capable of being placed in communication with at least one independent source of hydraulic pressure, called the actuating source, which is associated with the said single chamber and which comprises means for elastic return of the fluid which are intended, during the movement of the valve in a given direction, to recover the kinetic energy of the valve for its subsequent movement in the opposite direction.
  • the fluid return means are pneumatic.
  • the boosters are mechanical.
  • FIG. 1 There is shown in Figure 1 the assembly of a device 10 for actuating a valve 12 of a motor vehicle engine engine made according to the invention.
  • each valve 12 is formed of a tulip 14 and a rod or tail 16 which is integral with the tulip 14.
  • the tail 16 is integral with an actuator 18 which is controlled by a control unit, for example electronic (not shown), to cause the lifting and the return of the valve 12 on its seat (not shown).
  • the actuator 18 is in the form of a jack 20 which comprises a cylinder 22 inside which the tail 16 of the associated valve 12 is free to slide coaxially in a sealed manner, and inside which is arranged a movable piston 24, integral with the free end 26 of the tail of the valve 12.
  • the piston 24 defines in the cylinder 22 two opposite hydraulic pressure chambers which are fed with an incompressible hydraulic fluid FHI, for example of oil.
  • FHI incompressible hydraulic fluid
  • the piston 24 delimits more particularly in the cylinder 22 an upper pressure chamber 28 and a lower pressure chamber 30.
  • a pressure of said fluid FHI which is regulated by the control unit, is established inside each of the upper chambers 28 and lower 30, so that the pressure prevailing in one of the chambers 28 or 30 is alternatively higher / lower than the pressure prevailing in the other chamber, to alternately actuate the jack 20 and consequently the valve 12.
  • each chamber 28 or 30 of hydraulic pressure of the jack 22 is capable of being placed in communication with at least one independent source of hydraulic pressure, called the actuating source, which is associated with the only said chamber 28 or 30 and which comprises pneumatic means for elastic return of the fluid FHI which are intended, during the movement of the valve 12 in a given direction, to recover the kinetic energy of the valve 12 in view of its subsequent movement in the opposite direction.
  • the actuating source which is associated with the only said chamber 28 or 30 and which comprises pneumatic means for elastic return of the fluid FHI which are intended, during the movement of the valve 12 in a given direction, to recover the kinetic energy of the valve 12 in view of its subsequent movement in the opposite direction.
  • the device 10 preferably comprises two sources 32 and 34 of actuation. This provision is not limiting of the invention and the device 10 could comprise more than one actuation source associated with each of the pressure chambers 28 or 30 of the jack 12.
  • a conventional device for actuating valves by camshaft if it has the disadvantage of only allowing to benefit from a valve lift law, allows on the other hand to effectively control the speed closing the valve.
  • By giving the cams a high curvature profile in the area where they are supposed to control the closing of the valve it is possible to impose a reduced speed of the valve when approaching its seat, which reduces the risks of wear of this valve. seat and therefore increases the longevity of the device.
  • the device according to the invention makes it possible to remedy this drawback insofar as, when approaching its positions extremes of actuation, the valve 12 is driven at a virtually zero speed that can be controlled by a hydraulic head loss upstream of the solenoid valve EVD. This pressure drop can be a function of the position of the valve.
  • a first actuation source fully transfers its potential energy to the valve 12 in the form of kinetic energy, which at the end of the race is in turn transferred in form potential energy to a second source of actuation when the valve 12 reaches full opening.
  • the second actuation source completely transfers its potential energy to the valve 12 in the form of kinetic energy which, at the end of the stroke, is in turn transferred in the form of potential energy.
  • Another advantage of the device 10 according to the invention is that it consumes little hydraulic energy.
  • At least one of the hydraulic chambers 28 or 30 can be placed in communication with an additional source 36 called a source of discharge, in which the hydraulic fluid FHI is subjected to a reduced pressure.
  • the hydraulic fluid is capable of being reduced to a reduced pressure in one of the hydraulic pressure chambers so as to ensure the stability of the valve 12 in its extreme position associated with the establishment of a reduced pressure in said bedroom.
  • the regulation of the pressures P 28 , P 30 which are exerted on each of the opposite faces of the piston 24 to cause its upward or downward movements, is entirely managed by the control unit.
  • control unit is able to regulate the pressures P 28 , P 30 prevailing in the hydraulic pressure chambers 28 and 30 of the jack 20 by alternately controlling an actuating EVA solenoid valve which is interposed between one of the hydraulic pressure chambers 28 or 30 and its associated actuating source 32 or 34, and an EVD discharge solenoid valve which is interposed between said hydraulic pressure chamber 28 or 30 and the discharge source 36.
  • each actuation source 32 or 34 consists of a hydropneumatic accumulator 32 or 34 which comprises a casing 38, 40 within which a membrane 42, 44 defines a chamber 46, 48 and an actuating chamber 50, 52, the return chamber 46, 48 being insulated and filled with a compressible gas GC, and the actuating chamber 50, 52 being connected to the upper chamber 28 or to the corresponding lower chamber 30 of the associated jack 12 and filled with the incompressible fluid FHI.
  • the compressible gas GC which is contained in the return chambers 46 and 48 of the hydraulic accumulators 32 and 34 makes it possible to exert an elastic return action on the hydraulic fluid FHI contained in the chambers 50 and 52 and therefore constitutes a pneumatic spring that stores the kinetic energy of the valve 12.
  • the device 10 behaves like an oscillating device with electromechanical actuators, without the disadvantages, it is to say without presenting the disadvantages of important inertia.
  • the discharge source 36 comprises a reservoir 54 which is placed in communication with a casing (not shown) of the engine in which there is a reduced pressure "Pr".
  • the discharge source 36 can be connected to either of the upper chambers 28 or 30 of the jack 22 without modifying the operating principle of the device 10.
  • the rest position of the valve 12 that is to say at its position for which the hydraulic pressure in one of the chambers of the actuator 20 is reduced, corresponds to its closed position to ensure a perfect sealing the tulip 14 of the valve 12 on its seat.
  • the upper pressure chamber 28 of the jack 20 is capable of being placed in communication with the first hydropneumatic accumulator 32 for actuation or with the discharge source 36 via the respective solenoid valves EVA actuation and EVD discharge, and the lower pressure chamber 30 of the cylinder 20 communicates directly with the second hydropneumatic accumulator 34.
  • a non-return valve 56 can be interposed between the upper chamber 28 of the jack 20 and the first hydropneumatic accumulator 32.
  • each actuating chamber 50 or 52 of hydropneumatic accumulators 32 or 34 is connected to a device (not shown) for maintaining pressure which is capable of maintain said chamber at a respective set pressure Pc 32 and Pc 34 as the valve 12 is closed.
  • This device makes it possible in particular to compensate for the hydraulic energy losses experienced by the fluid during the movement of the valve 12, these losses being able in particular to be due to the friction of the valve stem 12 in the cylinder 22, to the friction of the piston 24 in the cylinder , and the losses of "fluid friction" type generated by the pressure forces exerted within the fluid FHI.
  • the invention also proposes a control method for ensuring the operation of the device 10 previously described.
  • the unit controls the closing of the EVA actuating solenoid valve and the opening of the discharge solenoid valve EVD, the first hydropneumatic accumulator 32 being maintained by the pressure device at a first set pressure Pc 32 and the second hydropneumatic accumulator 34 being maintained at a second setpoint pressure Pc 34 , the first setpoint pressure Pc 32 being greater than the second setpoint pressure Pc 34 and the second setpoint pressure Pc 34 being greater than the reduced pressure "Pr" of the crankcase.
  • the valve 12 is thus at rest and closed since the pressure P 28 which prevails in the upper chamber 28 of the jack 22 is equal to the reduced pressure "Pr" of the casing and is therefore less than the set pressure Pc 32 which prevails in the lower chamber of the cylinder.
  • the device is said to be “charged” since the actuating chamber 50 of the accumulator 32 is ready, notwithstanding the opening of the solenoid valve EVA, to set the reference pressure Pc 32 in the upper chamber 28 of the jack.
  • the unit controls the closing of the discharge solenoid valve EVD and the opening of the actuating solenoid valve EVA.
  • Pressure P 28 equal to the set pressure Pc 32 , which is now in the upper chamber 28 being greater than the set pressure Pc 34 which prevails in the lower chamber 30 of the cylinder, the resultant pressure forces exerted on the piston 24 causes its movement downwards in the direction of the opening of the valve 12.
  • valve 12 As the valve 12 opens, its movement causes the volume of the upper chamber 28 to increase, thus also the expansion of the gas GC contained in the return chamber 46 of the accumulator 32, and the decrease in the volume of the the lower chamber 30, and therefore also the compression of the gas GC contained in the return chamber 48 of the accumulator 34.
  • the acceleration of the valve 12 decreases to zero when the pressures prevailing in the two return chambers 46 and 48 are balanced. This position of the valve 12 corresponds to a maximum kinetic energy stored by the valve 12 and therefore at its highest speed. Then, as the displacement of the valve 12 continues, the deceleration of the valve 12 continues until it reaches zero speed at its fully open position.
  • the hydraulic fluid FHI is now substantially at the first setpoint pressure Pc 32 in the lower chamber 30 of the jack, and is substantially at the second setpoint pressure Pc 34 in the upper chamber 30 of the jack.
  • the unit then controls the closing of the EVA solenoid valve.
  • the valve 12 then begins its closing movement as soon as the increase of the pressure P 28 in the upper chamber 28 is sufficient.
  • the device comprises the non-return valve 56
  • the establishment of the pressure threshold of the latter makes it possible to determine a valve open time at full opening, which can possibly be reduced to a negligible value if the valve anti-return is weakly tared.
  • valve 12 The characteristics of the closing movement of the valve 12 are exactly similar to those of its opening movement. It should be noted that, as a result, the valve 12 is closed on its seat with a speed virtually zero, and therefore does not cause wear of the seat, which significantly increases the longevity of the engine considered.
  • a fourth step of completely closing the valve 12 which occurs when the valve 12 is closed again, the unit controls the opening of the solenoid valve EVD to reduce the residual pressure P 28 in the upper chamber 28 of the jack .
  • the device 10 is then brought back, as soon as the pressures are stabilized, to the configuration of the first resting step of the valve 12.
  • the valve 12 closes automatically after a determined period of time associated with the trigger threshold of this valve.
  • This configuration is particularly applicable in the case of a series vehicle engine for which a minimum consumption is sought.
  • the return of the fluid FHI in the actuating chamber 50 of the accumulator 50 is no longer provided by the non-return valve 56 but by the solenoid valve EVA. It is with a determined delay time that the control unit can control, during the third step, the reopening of the EVA actuating solenoid valve through which the hydraulic fluid circulates instead of circulating, as is the case in the particular embodiment of the invention, by the non-return valve 56. This delay time then corresponds to the time during which the valve 12 is locked in the open position.
  • the invention thus makes it possible to carry out a pneumatic control of the valves 12 of a series heat engine or of a motor operating at high speed which is reliable, inexpensive, and lowly consuming the energy of said engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (10)

  1. Vorrichtung (10) zum Betätigen der Ventile (12) eines Verbrennungsmotors eines Kraftfahrzeugs, jener Art, bei der jedes Ventil (12) eine Stange oder einen Schaft (16) aufweist, die bzw. der fest mit einem Stellglied (20) verbunden ist, das durch eine Steuereinheit dahingehend angesteuert wird, das Anheben und Rückholen des zugehörigen Ventils (12) zu bewirken, jener Art, bei der jedes Stellglied (20) in Form eines Zylinders ausgebildet ist, der einen Rohrzylinder (22) aufweist, in dem der Schaft (16) des zugehörigen Ventils (12) auf dichte Weise koaxial frei gleiten kann und in dem ein beweglicher Kolben (24) angeordnet ist, der fest mit dem freien Ende des Ventilschafts (16) verbunden ist und in dem Rohrzylinder (22) zwei gegenüberliegende Hydraulikdruckkammern, eine (28) obere und eine (30) untere, begrenzt, die jeweils mit einem inkompressiblen Fluid (FHI) gespeist werden und wobei in jeder davon abwechselnd ein Druck (P28, P30) des Fluids (FHI) hergestellt wird, der durch die Steuereinheit so reguliert wird, dass der in einer der Kammern (28, 30) herrschende Druck abwechselnd höher/niedriger ist als der in der anderen Kammer herrschende Druck, um abwechselnd den Zylinder (20) und das Ventil (12) zu betätigen,
    dadurch gekennzeichnet, dass jede Hydraulikdruckkammer (28, 30) des Zylinders (20) mit mindestens einer unabhängigen Hydraulikdruckquelle (32, 34), der so genannten Betätigungsquelle, in Verbindung gesetzt werden kann, die der einzigen Kammer (28, 30) zugeordnet ist und Mittel zum elastischen Rückholen des Fluids (FHI) aufweist, welche während der Bewegung des Ventils (12) in eine bestimmte Richtung die kinetische Energie des Ventils (12) im Hinblick auf seine spätere Bewegung in die entgegengesetzte Richtung wiedergewinnen sollen.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass die Mittel zum elastischen Rückholen pneumatisch sind.
  3. Vorrichtung (10) nach dem vorherigen Anspruch, dadurch gekennzeichnet, dass mindestens eine der hydraulischen Kammern (28, 30) mit einer zusätzlichen Quelle (36), der so genannten Ablassquelle, in der das Hydraulikfluid (FHI) einem verminderten Druck ausgesetzt wird, in Verbindung gesetzt werden kann.
  4. Vorrichtung (10) nach dem vorhergehenden Anspruch, dadurch gekennzeichnet, dass die Steuereinheit die in den Hydraulikdruckkammern (28, 30) des Zylinders (20) herrschenden Drücke (P28, P30) regulieren kann, indem sie abwechselnd ein zwischen einer der Hydraulikdruckkammern (28, 30) und ihrer zugehörigen Betätigungsquelle (32, 34) angeordnetes Betätigungsmagnetventil (EVA) und ein zwischen der Hydraulikdruckkammer (28, 30) und der Ablassquelle (36) angeordnetes Ablassmagnetventil (EVD) betätigt.
  5. Vorrichtung (10) nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass jede Betätigungsquelle (32, 34) aus einem hydropneumatischen Speicher (32, 34) besteht, der eine Umhüllung (38, 40) aufweist, in der eine Membran (42, 44) eine Rückholkammer (46, 48) und eine Betätigungskammer (50, 52) begrenzt, wobei die Rückholkammer (46, 48) isoliert und mit einem kompressiblen Gas (GC) gefüllt ist, und wobei die Betätigungskammer (50, 52) mit der entsprechenden oberen (28)/unteren (30) Kammer des zugehörigen Zylinders (20) verbunden und mit dem inkompressiblen Fluid (FHI) gefüllt ist.
  6. Vorrichtung (10) nach Anspruch 4 in Kombination mit Anspruch 5, dadurch gekennzeichnet, dass die obere Druckkammer (28) des Zylinders (20) durch das jeweilige Betätigungsmagnetventil (EVA) und Ablassmagnetventil (EVD) mit einem ersten hydropneumatischen Speicher (32) oder mit der Ablassquelle (36) in Verbindung gesetzt werden kann, und dass die untere Druckkammer (30) des Zylinders direkt mit einem zweiten hydropneumatischen Speicher (34) verbunden ist.
  7. Vorrichtung (10) nach Anspruch 6, dadurch gekennzeichnet, dass eine Rückschlagklappe (56) zwischen der oberen Kammer (28) des Zylinders (20) und dem ersten hydropneumatischen Speicher (32) angeordnet ist.
  8. Vorrichtung (10) nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass die Ablassquelle (36) ein Behältnis (54) aufweist, das mit einem Motorgehäuse in Verbindung gesetzt werden kann, in dem ein reduzierter Druck (Pr) herrscht.
  9. Vorrichtung (10) nach Anspruch 5, dadurch gekennzeichnet, dass jede Betätigungskammer (50,52) der hydropneumatischen Speicher (32, 34) mit einer Druckhaltevorrichtung verbunden ist, die sie auf einem Solldruck (Pc32, Pc34) halten kann, solange das Ventil (12) geschlossen ist.
  10. Verfahren zur Steuerung einer Vorrichtung (10) zur Betätigung der Ventile (12) eines Verbrennungsmotors eines Kraftfahrzeugs nach Anspruch 7 in Kombination mit Anspruch 8 oder 9,
    dadurch gekennzeichnet, dass
    - die Einheit in einem ersten Stadium, in dem das Ventil (12) im Ruhezustand ist, das Schließen des Betätigungsmagnetventils (EVA) und das Öffnen des Ablassmagnetventils (EVD) ansteuert, wobei der erste hydropneumatische Speicher (32) durch die Druckvorrichtung auf einem ersten Solldruck (Pc32) und der zweite hydropneumatische Speicher (34) auf einem zweiten Solldruck (Pc34) gehalten wird, wobei der erste Solldruck (Pc32) größer ist als der zweite Solldruck (Pc34) und der zweite Solldruck (Pc34) größer ist als der reduzierte Druck (Pr) des Motorgehäuses, dann
    - die Einheit in einem zweiten Stadium, in dem das Ventil (12) angehoben wird, das Schließen des Ablassmagnetventils (EVD) und das Öffnen des Betätigungsmagnetventils (EVA) ansteuert, dann
    - die Einheit in einem dritten Stadium, in dem das Ventil (12) zurückgeholt wird, das Schließen des Betätigungsmagnetventils (EVA) ansteuert, dann
    - die Einheit in einem vierten Stadium, in dem das Ventil (12) vollständig geschlossen wird, das Öffnen des Ablassmagnetventils (EVD) bis zum ersten Ruhestadium ansteuert.
EP01974436A 2000-10-05 2001-10-05 Vorrichtung zum betätigen der ventile und steuerungsverfahren dafür Expired - Lifetime EP1341992B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0012712 2000-10-05
FR0012712A FR2815075B1 (fr) 2000-10-05 2000-10-05 Dispositif d'actionnement de soupapes, et procede de commande pour un tel dispositif
PCT/FR2001/003069 WO2002029216A1 (fr) 2000-10-05 2001-10-05 Dispositif d'actionnement de soupapes, et procede de commande pour un tel dispositif

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Publication Number Publication Date
EP1341992A1 EP1341992A1 (de) 2003-09-10
EP1341992B1 true EP1341992B1 (de) 2006-07-26

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US (1) US6871618B2 (de)
EP (1) EP1341992B1 (de)
JP (1) JP2004510907A (de)
DE (1) DE60121796T2 (de)
FR (1) FR2815075B1 (de)
WO (1) WO2002029216A1 (de)

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DE60121796D1 (de) 2006-09-07
US6871618B2 (en) 2005-03-29
JP2004510907A (ja) 2004-04-08
EP1341992A1 (de) 2003-09-10
FR2815075B1 (fr) 2003-01-24
WO2002029216A1 (fr) 2002-04-11
FR2815075A1 (fr) 2002-04-12
DE60121796T2 (de) 2007-08-02
US20040112312A1 (en) 2004-06-17

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