EP1577508A1 - Ventilrückholvorrichtung und Motor mit solcher Vorrichtung - Google Patents

Ventilrückholvorrichtung und Motor mit solcher Vorrichtung Download PDF

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Publication number
EP1577508A1
EP1577508A1 EP05290548A EP05290548A EP1577508A1 EP 1577508 A1 EP1577508 A1 EP 1577508A1 EP 05290548 A EP05290548 A EP 05290548A EP 05290548 A EP05290548 A EP 05290548A EP 1577508 A1 EP1577508 A1 EP 1577508A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
supply
cylinder
channel
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
Application number
EP05290548A
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English (en)
French (fr)
Other versions
EP1577508B1 (de
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/de
Application granted granted Critical
Publication of EP1577508B1 publication Critical patent/EP1577508B1/de
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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 the valves in internal combustion engines.
  • It relates to a device for returning a valve as well as an internal combustion engine equipped with such device.
  • 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 chamber sealed which contains a compressible fluid at a corresponding predetermined minimum setting pressure at the fully closed position of the valve.
  • valve control system so proposed is an advance over the document system FR-2 529 616, the structure implemented to ensure the pressure regulation is however relatively complex, while its responsiveness, insufficient, is reveals penalizing during sudden variations of regime engine.
  • the invention aims in particular to remedy disadvantages mentioned above, by proposing a reminder allowing precise regulation of the force of recall to which the valve is subjected and which, while with increased responsiveness (in other words, time reduced response, especially during sudden variations engine speed), further reduces 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 feeding through a diversion channel.
  • a check valve placed on the supply channel, the channel of bypass being connected to the supply upstream of this check 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 when the engine speed.
  • the invention proposes a internal combustion engine equipped with a recall as presented above.
  • FIG. 1 shows a device for reminder 1 of a valve 2 of an internal combustion engine of which only the intake manifold 3 has been shown (or exhaust) whose valve 2 controls the opening and closing.
  • the valve 2 has a rod 4 which ends, at one of its ends, by a head 5 adapted to bear against a seat 6 which forms the mouth of the intake manifold 3.
  • Rod 4 ends, at its opposite end, by a tail 7 shaped into 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, solidary of the valve stem 4, is slidably mounted in a cylinder 11.
  • Device 1 also includes a power supply 12 in fluid under pressure, fluidly connected to the cylinder 11 by a feed channel 13 on which is placed a check valve 14.
  • the device 1 further comprises a check valve overpressure 15 fluidly connected, on the one hand to the cylinder 11 through an evacuation channel 16 and, on the other hand, feeding 12 by a bypass channel 17 which, as this is visible in Figures 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 secured to a valve 20.
  • the piston 19 divides the cylinder 18 in two rooms insulated in a sealed manner, namely a bedroom said overpressure 21, in which the channel of branch 17, and a relaxation chamber 22 in which opens the evacuation channel 16 and a release channel the open air 23 thanks to which the pressure prevailing in the relaxation chamber 22 is constantly equal to the pressure atmospheric.
  • the piston 19 is movably mounted between a so-called closure, illustrated in Figure 1, in which the valve 20 closes the discharge channel 16, and a so-called opening position, illustrated in Figure 3, in which the valve 20 is spaced from the evacuation channel 16 that she puts in communication with the Chamber of relaxation 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.
  • valve 15 is equipped with a return spring 24 which permanently urges the piston 19 towards its position of closing.
  • 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 according to 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 expansion chamber 22.
  • valve is represented at its top dead center (TDC see Figure 7) where, pressed against 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 by compared to the previous cycle, its stiffness being superior.
  • 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 points A “and B”, then between points B “and C”, dashed line curve), the pneumatic spring 8 however having a stiffness less than the stiffness it exhibited 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 which results in the controller 25 controlling the decrease in the supply pressure P A , the minimum and maximum pressures then being set at lower values P m2 and P M2 , respectively, at 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 maximum pressure P M , as a function of the supply pressure P A.
  • This regulation responds to an affine law, which which makes it possible to regulate precisely the stiffness of the pneumatic spring 8 depending in particular, as presented above, the engine speed.

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 Ventilrückholvorrichtung und Motor mit solcher Vorrichtung Expired - Fee Related EP1577508B1 (de)

Applications Claiming Priority (2)

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

Publications (2)

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

Family

ID=34834186

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05290548A Expired - Fee Related EP1577508B1 (de) 2004-03-17 2005-03-11 Ventilrückholvorrichtung und Motor mit solcher Vorrichtung

Country Status (8)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020038574A1 (en) * 2018-08-23 2020-02-27 Volvo Truck Corporation Cylinder valve assembly with valve spring venting arrangement

Families Citing this family (4)

* 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 (de) * 2009-01-20 2013-03-27 BRP-Powertrain GmbH & Co. KG Luftfedersystem für Verbrennungsmotoren
EP2211031B1 (de) * 2009-01-22 2013-07-10 BRP-Powertrain GmbH & Co. KG Luftfeder mit Kappe
EP3406866A1 (de) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Hydraulischer antrieb zum beschleunigen und abbremsen dynamisch zu bewegender bauteile

Citations (5)

* 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
DE3808542A1 (de) * 1987-03-26 1988-10-06 Volkswagen Ag Ventiltrieb fuer ein gaswechselventil einer brennkraftmaschine
DE4220689A1 (de) * 1991-06-27 1993-01-07 Man B & W Diesel Gmbh Sperrluftsystem bei einem verbrennungsmotor
US5664527A (en) * 1993-10-29 1997-09-09 Automobiles Peugeot Pneumatic valve recoil system for internal combustion engines
EP1132581A1 (de) * 2000-03-10 2001-09-12 Sagem Sa Elektromagnetventil mit Pneumatikfeder und Kniehebelmechanismus

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2529616B1 (fr) 1982-06-30 1987-03-27 Renault Sport Systeme de rappel pneumatique de soupape pour moteur a combustion interne
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
DE69211942T2 (de) 1991-08-21 1996-10-31 Honda Motor Co Ltd Hubventilsteuerungsvorrichtung für Brennkraftmaschine
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
JP2000224405A (ja) * 1999-01-29 2000-08-11 Dainippon Screen Mfg Co Ltd 画像処理方法
US6738706B2 (en) * 2002-06-19 2004-05-18 Ford Global Technologies, Llc Method for estimating engine parameters

Patent Citations (5)

* 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
DE3808542A1 (de) * 1987-03-26 1988-10-06 Volkswagen Ag Ventiltrieb fuer ein gaswechselventil einer brennkraftmaschine
DE4220689A1 (de) * 1991-06-27 1993-01-07 Man B & W Diesel Gmbh Sperrluftsystem bei einem verbrennungsmotor
US5664527A (en) * 1993-10-29 1997-09-09 Automobiles Peugeot Pneumatic valve recoil system for internal combustion engines
EP1132581A1 (de) * 2000-03-10 2001-09-12 Sagem Sa Elektromagnetventil mit Pneumatikfeder und Kniehebelmechanismus

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020038574A1 (en) * 2018-08-23 2020-02-27 Volvo Truck Corporation Cylinder valve assembly with valve spring venting arrangement
US11619148B2 (en) 2018-08-23 2023-04-04 Volvo Truck Corporation Cylinder valve assembly with valve spring venting arrangement

Also Published As

Publication number Publication date
US7249580B2 (en) 2007-07-31
DE602005000844T2 (de) 2007-12-13
FR2867807B1 (fr) 2006-07-07
JP2005264942A (ja) 2005-09-29
EP1577508B1 (de) 2007-04-11
DE602005000844D1 (de) 2007-05-24
US20050217619A1 (en) 2005-10-06
ES2285652T3 (es) 2007-11-16
FR2867807A1 (fr) 2005-09-23
AU2005201158A1 (en) 2005-10-06
CA2500689A1 (fr) 2005-09-17

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