EP1577508B1 - Dispositif de rappel d'une soupape et moteur équipé d'un tel dispositif - Google Patents

Dispositif de rappel d'une soupape et moteur équipé d'un tel dispositif Download PDF

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Publication number
EP1577508B1
EP1577508B1 EP05290548A EP05290548A EP1577508B1 EP 1577508 B1 EP1577508 B1 EP 1577508B1 EP 05290548 A EP05290548 A EP 05290548A EP 05290548 A EP05290548 A EP 05290548A EP 1577508 B1 EP1577508 B1 EP 1577508B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
feed
cylinder
return
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
Application number
EP05290548A
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German (de)
English (en)
French (fr)
Other versions
EP1577508A1 (fr
Inventor
Patrice Martinez
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Safran Aerosystems SAS
Original Assignee
Intertechnique SA
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Intertechnique SA filed Critical Intertechnique SA
Publication of EP1577508A1 publication Critical patent/EP1577508A1/fr
Application granted granted Critical
Publication of EP1577508B1 publication Critical patent/EP1577508B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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

Definitions

  • the invention relates to the control of valves in internal combustion engines.
  • It relates to a valve return device and an internal combustion engine equipped with such a device.
  • the motors are equipped with return devices which comprise, for each valve, a spring which urges it permanently in the direction of its closure (that is to say in the direction of the cam corresponding).
  • the proposed system comprises a piston integral with a valve stem and sliding in a cylinder, the piston, the valve stem and the cylinder forming a sealed chamber which encloses a compressible fluid at a predetermined minimum setting pressure corresponding to the fully closed position of the valve.
  • valve control system so proposed is an advance over the system of the document FR-2 529 616, the structure used to provide pressure control is however relatively complex, while its reactivity, insufficient, is detrimental to sudden changes in engine speed.
  • the invention aims in particular to overcome the aforementioned drawbacks, by proposing a return device for precise regulation of the return force to which the valve is subjected and which, while having increased reactivity (in other words a reduced response time, especially during sudden changes in engine speed), can further reduce the risk of panic valves.
  • the pressure relief valve is provided with a return spring, in which case the constant P 2 is the set pressure of said pressure relief valve provided by said return spring.
  • the pressure relief valve is for example connected to the supply by a bypass channel.
  • non-return valve placed on the supply channel, the bypass channel being connected to the supply upstream of the non-return valve.
  • the power supply can be controlled to regulate the supply pressure according to one or more determined parameters, such as the engine speed.
  • the power supply is preferably controlled to increase the supply pressure as the engine speed increases.
  • the invention proposes an internal combustion engine equipped with a return device as presented above.
  • FIG. 1 shows a return device 1 of a valve 2 of an internal combustion engine of which only the intake (or exhaust) pipe 3 has been shown, the valve 2 of which controls the opening and the closing.
  • the valve 2 comprises a rod 4 which ends, at one of its ends, with a head 5 able to bear against a seat 6 which forms the mouth of the tubing of admission 3.
  • the rod 4 ends, at its opposite end, with a tail 7 shaped as a cam follower which is held in abutment by a pneumatic spring 8 (described below) against a cam 9 of a camshaft whose rotation controls the opening and closing of the valve 2.
  • the valve 2 is provided with a piston 10 which, secured to the valve stem 4, is slidably mounted in a cylinder 11.
  • the device 1 also comprises a supply 12 of fluid under pressure, fluidly connected to the cylinder 11 by a supply channel 13 on which is placed a check valve 14.
  • the device 1 further comprises a pressure relief valve 15 fluidly connected, on the one hand to the cylinder 11 by a discharge channel 16 and, on the other hand, to the supply 12 by a bypass channel 17 which, as can be seen in FIGS. 1 to 6, is connected to the supply 12 upstream of the non-return valve 14.
  • the pressure relief valve 15 comprises a cylinder 18 in which slides a piston 19 which is integral with a valve 20.
  • the piston 19 divides the cylinder 18 into two sealed chambers, namely a so-called overpressure chamber 21, into which the bypass channel 17, and an expansion chamber 22 in which the discharge channel 16 opens and a venting channel 23 through which the pressure in the expansion chamber 22 is constantly equal to atmospheric pressure.
  • the piston 19 is movably mounted between a so-called closing position, illustrated in FIG. 1, in which the valve 20 closes off the evacuation channel 16, and a so-called opening position, illustrated in FIG. 3, in which the valve 20 is separated from the evacuation channel 16 that it thus communicates with the expansion chamber 22.
  • S P is the area of the surface of the piston 19 turned on the side of the pressure chamber 21, and S S the area of the surface of the valve 20 turned towards the side of the discharge channel 16.
  • the pressure relief valve 15 is equipped with a return spring 24 which constantly urges the piston 19 to its closed position.
  • the supply 12 comprises a pressure regulator connected via a channel 26 to a source of pressurized fluid (not shown), this regulator being arranged to vary the pressure in the feed channel 13 as a function of one or more determined parameters such as the engine speed, which is characterized by the rotational speed - denoted V R - of the motor shaft.
  • the pressure relief valve 15 is designed to limit the pressure P prevailing in the cylinder 11 to the maximum pressure P M : indeed, when the pressure P reaches or exceeds this maximum pressure P M , the fluid of the discharge channel 16, in from the cylinder 11, exerts on the valve 20 a pressure which compensates the pressure P M prevailing in the pressure chamber 21, which tends to move the piston 19, initially in its closed position, to its open position, putting thus the evacuation channel 16 in communication with the chamber of relaxation 22.
  • valve is shown at its top dead center (TDC see Figure 7) where, pressed against the seat 6, it closes the intake manifold 3.
  • check valves 14 and of overpressure 15 makes it possible to limit between two extreme values (corresponding, respectively, to the minimum pressure P m and to the maximum pressure P M , the restoring force exerted on the valve 2 by the air spring 8 constituted by the fluid present in the cylinder 11.
  • FIG. 8 shows a diagram illustrating the pressure P of the fluid contained in the cylinder 11 as a function of the displacement h of the piston 10, illustrating three successive cycles of opening / closing of the valve 2, between which it has been controlled, first an increase in the supply pressure P A consecutive to the increase in the engine speed, then a decrease in the supply pressure P A following a decrease in engine speed.
  • the pressure P is equal to the minimum pressure P m1 corresponding to the initial supply pressure P A.
  • P A also corresponds to a maximum pressure P M1 , which reigns in the overpressure chamber 21.
  • the opening phase of the valve 2 is as previously described (between the points A and B, curve in solid lines), the pressure relief valve 15 intervening (between points B and C) when the pressure P reaches the maximum pressure. P M1 .
  • the regulator 25 controls (arbitrarily) an increase in the engine speed in the closing phase of the valve 2, corresponding to the expansion of the fluid (between the points C and D of the diagram of FIG. 8): the regulator 25 then controls the increase of the supply pressure P A.
  • the air spring 8 is thus modified with respect to the previous cycle, its stiffness being greater.
  • the opening phase of the valve is as described above (points B 'and C', dotted line).
  • a reduction of the engine speed is controlled (arbitrarily): the regulator 25 then controls a decrease in the supply pressure P A , the the minimum pressure is then established at a new value P m3 while the maximum pressure prevailing in the booster chamber 21 is set at a new value P M3 , these new values P m3 and P M3 being, respectively, less than initial values P m1 and P M1 .
  • the opening phase of the valve 2 is then repeated as before (between the points A “and B”, then between the points B “and C”, curve in phantom), the air spring 8 however having a stiffness less than the stiffness that it presented during the two previous cycles;
  • the regulator 25 then controls an increase in the supply pressure P A , the minimum and maximum pressures then returning to their respective initial values P m1 and P M1 .
  • the rotation of the cam 9 causes, as previously described, the compression of the fluid present in the cylinder 11. However, it occurs at a given moment (point B 1 in the diagram of FIG. 9) where the pressure P n ' has not yet reached the maximum value P M1 , a sudden drop in engine speed resulting in the control by the regulator 25, of the decrease of the supply pressure P A , the minimum and maximum pressures then being set to values P m2 and P M2 lower, respectively, to the initial values P m1 and P M1 .
  • the overpressure immediately causes the valve 15 to open, the pressure P falling until reaching the new value of the maximum pressure P M2 (point B 2 ).
  • the rest of the cycle is (momentarily) as previously described.
  • the pressure P is kept constant and equal to the value P M2 to the bottom dead point (point C) where the closure of the pressure relief valve 15 occurs, the cycle then initiating its opening phase of the valve 2.
  • the non-return valve 14 then enters into action, the pressure P then rising abruptly to the new minimum value P m3 (point D 2 ), which value it conserves up to the top dead point (point A ').
  • the return device 1 makes it possible to regulate, not only the minimum pressure P m required in the cylinder 11, but also the pressure maximum P M, depending on the supply pressure P A.
  • This regulation responds to a law of the affine type, which makes it possible to precisely regulate the stiffness of the air spring 8 in particular as a function of the engine speed, as shown above.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP05290548A 2004-03-17 2005-03-11 Dispositif de rappel d'une soupape et moteur équipé d'un tel dispositif Expired - Lifetime EP1577508B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0402764 2004-03-17
FR0402764A FR2867807B1 (fr) 2004-03-17 2004-03-17 Dispositif de rappel d'une soupape et moteur equipe d'un tel dispositif

Publications (2)

Publication Number Publication Date
EP1577508A1 EP1577508A1 (fr) 2005-09-21
EP1577508B1 true EP1577508B1 (fr) 2007-04-11

Family

ID=34834186

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05290548A Expired - Lifetime EP1577508B1 (fr) 2004-03-17 2005-03-11 Dispositif de rappel d'une soupape et moteur équipé d'un tel dispositif

Country Status (8)

Country Link
US (1) US7249580B2 (es)
EP (1) EP1577508B1 (es)
JP (1) JP2005264942A (es)
AU (1) AU2005201158A1 (es)
CA (1) CA2500689A1 (es)
DE (1) DE602005000844T2 (es)
ES (1) ES2285652T3 (es)
FR (1) FR2867807B1 (es)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3841287B1 (en) * 2018-08-23 2024-02-14 Volvo Truck Corporation Cylinder valve assembly with valve spring venting arrangement

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007022652A1 (de) * 2007-05-15 2008-11-20 Daimler Ag Gaswechselventilbetätigungsvorrichtung
EP2208870B1 (en) 2009-01-20 2013-03-27 BRP-Powertrain GmbH & Co. KG Air spring system for an internal combustion engine
EP2211031B1 (en) * 2009-01-22 2013-07-10 BRP-Powertrain GmbH & Co. KG Air spring with cap
EP3406866A1 (de) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Hydraulischer antrieb zum beschleunigen und abbremsen dynamisch zu bewegender bauteile
AT526848B1 (de) * 2023-04-28 2024-08-15 Avl List Gmbh Pneumatisches ventilfedersystem

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2342003A (en) * 1941-11-12 1944-02-15 Wright Aeronautical Corp Pressure operated valve gear
FR2529616B1 (fr) 1982-06-30 1987-03-27 Renault Sport Systeme de rappel pneumatique de soupape pour moteur a combustion interne
DE3808542C2 (de) * 1987-03-26 1994-03-24 Volkswagen Ag Ventiltrieb für ein Gaswechselventil einer Brennkraftmaschine
DK167499B1 (da) * 1991-06-27 1993-11-08 Man B & W Diesel Gmbh Spaerreluftarrangement ved en forbraendingsmotor
DE69211942T2 (de) 1991-08-21 1996-10-31 Honda Motor Co Ltd Hubventilsteuerungsvorrichtung für Brennkraftmaschine
JPH0559916A (ja) * 1991-08-27 1993-03-09 Honda Motor Co Ltd 内燃機関のエアバルブスプリングシステム
JPH0519506U (ja) * 1991-08-27 1993-03-12 本田技研工業株式会社 内燃機関のエアバルブスプリング装置
JPH0559917A (ja) * 1991-08-27 1993-03-09 Honda Motor Co Ltd 内燃機関のエアバルブスプリングシステム
JP3135634B2 (ja) * 1991-09-13 2001-02-19 本田技研工業株式会社 内燃エンジンの空気ばね式動弁装置
FR2711729B1 (fr) * 1993-10-29 1995-12-01 Peugeot Système de rappel pneumatique de soupape pour moteur à combustion interne.
JP2000224405A (ja) * 1999-01-29 2000-08-11 Dainippon Screen Mfg Co Ltd 画像処理方法
FR2806146B1 (fr) * 2000-03-10 2002-10-25 Sagem Dispositif de commande electromagnetique de soupapes, a ressorts pneumatiques
US6738706B2 (en) * 2002-06-19 2004-05-18 Ford Global Technologies, Llc Method for estimating engine parameters

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3841287B1 (en) * 2018-08-23 2024-02-14 Volvo Truck Corporation Cylinder valve assembly with valve spring venting arrangement

Also Published As

Publication number Publication date
ES2285652T3 (es) 2007-11-16
EP1577508A1 (fr) 2005-09-21
AU2005201158A1 (en) 2005-10-06
JP2005264942A (ja) 2005-09-29
US7249580B2 (en) 2007-07-31
US20050217619A1 (en) 2005-10-06
DE602005000844T2 (de) 2007-12-13
FR2867807B1 (fr) 2006-07-07
FR2867807A1 (fr) 2005-09-23
CA2500689A1 (fr) 2005-09-17
DE602005000844D1 (de) 2007-05-24

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