EP1367231A1 - Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules - Google Patents

Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules Download PDF

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Publication number
EP1367231A1
EP1367231A1 EP03009499A EP03009499A EP1367231A1 EP 1367231 A1 EP1367231 A1 EP 1367231A1 EP 03009499 A EP03009499 A EP 03009499A EP 03009499 A EP03009499 A EP 03009499A EP 1367231 A1 EP1367231 A1 EP 1367231A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
valve stroke
rocker arm
control according
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
EP03009499A
Other languages
German (de)
English (en)
Other versions
EP1367231B1 (fr
Inventor
Dieter Maisch
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
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 Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP1367231A1 publication Critical patent/EP1367231A1/fr
Application granted granted Critical
Publication of EP1367231B1 publication Critical patent/EP1367231B1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L13/0047—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction the movement of the valves resulting from the sum of the simultaneous actions of at least two cams, the cams being independently variable in phase in respect of each other

Definitions

  • the invention relates to a valve lift control for internal combustion engines of motor vehicles according to the preamble of claim 1.
  • valve lift controls valves of an internal combustion engine of motor vehicles only so wide open that for the respective power requirement the corresponding amount of fuel in the engine Combustion chamber is injected.
  • the control shaft acts on Actuator in the form of a lever that acts on the valve stem. This mechanical control element is prone to failure and does not allow any exact setting of the valve stroke.
  • the invention has for its object the generic valve lift control to be designed so that the valve lift is structurally simpler Way can be set accurately and reliably.
  • the control device hydraulically operated. Since the hydraulic medium in one Motor vehicle is present anyway, the control device can be simple be supplied with the necessary hydraulic medium. With the Control device can set the stroke of the valve easily and accurately become.
  • FIG. 1 shows a cylinder head 1 of an internal combustion engine, in which a different one depending on the type of engine Number of combustion chambers and associated valves 2 are provided is.
  • Fig. 1 one of these valves 2 is shown, the one valve plate 3, with which an inlet opening 4 is closed in the combustion chamber can be.
  • the valve plate 3 sits at the end of a valve stem 5, against the force of at least one compression spring 6 in a Open position can be postponed.
  • the valve stem 5 instructs its end opposite the valve plate 3 has a spring plate 7, on which one end of the compression spring 6 is supported. you the other end is supported on the cylinder head side.
  • valve plate 3 By the compression spring 6 in its shown in Fig. 1 Pulled closed position.
  • the end 8 projecting over the spring plate 7 the valve stem 5 is dome-shaped and lies in one pan-like receptacle 9 at the free end of an arm 10 of a two-armed rocker arm 11. It is transversely to its imaginary Swivel axis in a fork 12 secured in position on the cylinder head 1 is provided.
  • the other arm 13 of the rocker arm 11 lies on one Actuating cylinder 14, which in a bore 15 in the cylinder head 1 is slidably mounted.
  • the actuating cylinder 14 takes a hollow piston 16, which bears against a cam 17 of a control shaft 18.
  • the hollow piston 16 receives at least one compression spring 19, which is with one end on a bottom 20 of the hollow piston 16 and with her the other end is supported on a bottom 21 of the actuating cylinder 14.
  • the hollow piston 16 is always so loaded by the compression spring 19 that he with his bottom 20 on a cam 22 of the cam 17 of the Control shaft 18 is present.
  • the hollow piston 16 is sealed in the actuating cylinder 14 slidably guided. Since the hollow piston 16 the compression spring 19 records, results in a very compact design.
  • part 16 also be solid. Then because of the compression spring 19, the between the end face of part 16 and the bottom 21 of the actuating cylinder 14 is given a greater length of the control device.
  • the actuating cylinder 14 is part of its length from an annular space 23 surrounded, which is provided in the cylinder head 1 and in the a bore 24 opens.
  • the annular space 23 is by a Diameter enlarged section of the bore 15 is formed.
  • the actuating cylinder 14 has a small distance from its bottom 21 arranged in its cylinder wall 25 distributed over the circumference Passages 26, preferably bores, through which the annular space 23 is connected to the interior 27 of the actuating cylinder 14.
  • the two ends of the lever arms 10, 13 are in the direction of the Valve stem 5 or the actuating cylinder 14 angled.
  • On the other Side of the rocker arm 11 is provided with an increase 28, which extends over most of the length of the rocker arm 11 and on which is a camshaft 29. With it the rocker arm 11 in still to be described pivoted to open the valve 2.
  • the rocker arm 11 is not fixed, but lies with the ends his arms 10, 13 on the valve stem 5 or on the actuating cylinder 14.
  • Fig. 1 shows the initial position of the valve lift control
  • the Cam 30 of the camshaft 29 does not engage the rocker arm 11 is.
  • the control shaft 18 is rotated to a position in which a contact area 31 between the control curve 22 and the bottom 20 of the Hollow piston 16 the greatest distance from the axis 32 of the control shaft 18 has.
  • valve 2 is closed.
  • the hollow piston 16 is at a distance from the bottom 21 of the actuating cylinder 14, the Bores 26 the annular space 23 with the interior 27 of the actuating cylinder 14 and connect to the interior 33 of the hollow piston 16. If the camshaft 29 is rotated in the direction of arrow 34 (FIG. 2), it arrives the cam 30 in the region of the arm 13 on the rocker arm 11.
  • Fig. 4 shows the maximum valve lift. It is reached when the Camshaft 29 is rotated so far that the cam 30 in the direction of the rocker arm 11 protrudes the farthest. In this position (Fig. 4) the rocker arm 11 is pivoted furthest counterclockwise, so that the valve stem 5 is shifted farthest. The valve 2 has thus performed the largest stroke. The valve plate 3 is the farthest from its valve seat.
  • valve clearance compensation is also performed at the same time reached so that the valves reliably opened and getting closed.
  • the force of the compression spring 19 in the actuating cylinder 14 is significantly less than the force of the compression spring 6 with which the valve 2 is loaded.
  • the Force of the compression spring 19 is so great in any case that a safe Applying the actuating cylinder 14 and the hollow piston 16 on Rocker arm 11 or on the cam 22 of the control shaft 18 guaranteed is.
  • the running play between the hollow piston 16 and the actuating cylinder 14 is so low that there is a sealing function.
  • the hydraulic medium therefore does not escape to the outside, so that leakage losses are avoided or are only negligibly small.
  • a lever 11 For each cylinder of the internal combustion engine is a lever 11 with the corresponding valve lift control provided. On the control shaft Depending on the tax strategy, 18 can have several or only one control lane 22 lie.
  • the valve lift can be changed with the control shaft 18.
  • the Valve stroke can be set so that in the respective combustion chamber only as much fuel is injected as for the current one Power of the internal combustion engine is required.
  • the distance between the hollow piston 16 can be changed by the axis 32 of the control shaft 18, each according to the rotational position of the control shaft.
  • 1 to 4 is the control shaft 18 rotated so that the hollow piston 16 the greatest distance from the Axis 32 of the control shaft 18 has.
  • 5 and 6 show the case that the hollow piston 16 from the axis 32 of the control shaft 18 smallest distance.
  • the control shaft 18 is for this purpose from the position 1 to 4 have been rotated clockwise until the Control shaft 5 has reached the position shown in FIGS. 5 and 6.
  • the Hollow piston 16 lies with its base 20 under the force of the compression spring 19 on the control cam 22 of the cam 17 of the control shaft 18.
  • the hollow piston 16 is pushed out of the actuating cylinder 14 so far that the end face 35 of the hollow piston 16 in the area below of the bores 26 in the cylinder wall 25 of the actuating cylinder 14 lies.
  • the interiors 27, 33 of the actuating cylinder 14 and the hollow piston 16 are thus connected to the annular space 23 and the bore 24.
  • the rocker arm 11 in the manner described with reference to FIGS. 1 to 4 in a clockwise direction tilted so that the actuating cylinder 14 relative to the hollow piston 16 is moved against the force of the compression spring 19.
  • the Hollow piston 16 is supported on the control cam 22 of the control shaft 18 from. Since the control shaft 18 is rotated so that the distance between the hollow piston 16 and the axis 32 of the control shaft 18 is minimal, the actuating cylinder 14 is compared to the position of the control shaft 1 to 4 significantly shifted until the holes 26 of the actuating cylinder 14 closed by the hollow piston 16 are. Then the actuating cylinder 14 and the hollow piston 16 act in the described way as a fixed bearing for the rocker arm 11.
  • the stroke of the valve 2 between the maximum stroke (Fig. 1 to 4) and the zero stroke (Fig. 5 and 6) can be set. If the control shaft 18 intermediate positions between the maximum position (Fig. 1 to 4) and the minimum position (Fig. 5 and 6) takes, the stroke of the valve 2 between the Maximum stroke according to FIGS. 1 to 4 and the zero stroke according to FIGS. 5 and 6 can be set continuously. This can be very easy Way exactly the amount of fuel to be set for the respective power requirement of the internal combustion engine in the combustion chamber is injected.
  • the actuating cylinder 14 lies on the control cam 22 of the cam 17 Control shaft 18 on. It is rotated so that the actuating cylinder 14 the has the smallest distance from the axis 32 of the control shaft 18.
  • the end face 35 of the hollow piston 16 lies at a distance from the bores 26 in the cylinder wall 25 of the actuating cylinder 14.
  • the bores 26, which are closely adjacent according to the previous embodiment are provided to the bottom of the actuating cylinder 14 are thus not closed by the hollow piston 16.
  • the hydraulic medium can from the bore 24 into the annular space 23 and from there the bores 26 into the interior spaces 27 and 33 of the actuating cylinder 14 and the hollow piston 16 arrive.
  • valve 2 closes again. by the valve stem 5 via the spring plate 7 from the compression spring 6 is pushed back.
  • the rocker arm 11 is here clockwise tilted.
  • the Cam 30 of the camshaft 29 again in such a position that the Compression spring 19 pushes back the hollow piston 16 and thereby the rocker arm 11 returns to the starting position according to FIG. 7.
  • the Hollow piston 16 releases the holes 26 in the actuating cylinder 14, that is Hydraulic medium sucked out of the bore 24.
  • the control shaft 18 In order to change the stroke of the valve 2, the control shaft 18 turned. Depending on the rotational position of the control shaft 18 or its cam 17, the stroke of the valve 2 is varied. This ensures that the fuel is only in such an amount in the combustion chamber the internal combustion engine is injected, as for the respective Power of the internal combustion engine is necessary.
  • the hydraulic medium required for the operation of the control device 14, 16 is necessary, can also be in a preloaded memory are located.
  • the hollow piston 16 gives the bores 26 in the actuating cylinder 14 free, the hydraulic medium from the preloaded memory sucked. Conversely, the hydraulic medium can shrink of the interior 27, 33 of the control device 14, 16 in the memory to be ousted.
  • the circuit of the hydraulic medium with the preloaded accumulator can be self-contained. But it is also possible that preloaded accumulator via a check valve with the engine oil circuit to connect and dine on it. This will in particular leakage compensation achieved.
EP03009499A 2002-05-10 2003-04-28 Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules Expired - Lifetime EP1367231B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10220692A DE10220692A1 (de) 2002-05-10 2002-05-10 Ventilhubsteuerung für Verbrennungsmotoren von Kraftfahrzeugen
DE10220692 2002-05-10

Publications (2)

Publication Number Publication Date
EP1367231A1 true EP1367231A1 (fr) 2003-12-03
EP1367231B1 EP1367231B1 (fr) 2005-04-20

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EP03009499A Expired - Lifetime EP1367231B1 (fr) 2002-05-10 2003-04-28 Système de contrôle de levée de soupape pour moteurs à combustion interne de véhicules

Country Status (4)

Country Link
US (1) US6779497B2 (fr)
EP (1) EP1367231B1 (fr)
DE (2) DE10220692A1 (fr)
ES (1) ES2242120T3 (fr)

Families Citing this family (10)

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US7012315B1 (en) * 2000-11-01 2006-03-14 Micron Technology, Inc. Frame scale package using contact lines through the elements
US7401584B2 (en) * 2004-07-01 2008-07-22 Schaeffler Kg Adjustable engine
DE102004060433A1 (de) * 2004-12-14 2006-07-06 Daimlerchrysler Ag Nockenfolger zur Betätigung eines Gaswechselventiles einer Brennkraftmaschine
DE102006007121A1 (de) * 2006-02-16 2007-08-23 Daimlerchrysler Ag Gaswechselventilbetätigungsvorrichtung
CN101225759B (zh) * 2008-01-25 2010-06-09 许小法 可变气门升程装置
CN102979589B (zh) * 2011-09-06 2015-05-20 北汽福田汽车股份有限公司 发动机配气机构、发动机及汽车
DE102011114588A1 (de) * 2011-09-30 2013-04-04 Thyssenkrupp Presta Teccenter Ag Ventiltrieb für Brennkraftmaschinen mit verstellbarer Nockenwelle
JP6036757B2 (ja) * 2014-07-16 2016-11-30 トヨタ自動車株式会社 内燃機関の可変動弁機構
EP3000996B1 (fr) * 2014-09-23 2017-05-10 FPT Motorenforschung AG Ensemble de commande auxiliaire destinée à commander l'ouverture/la fermeture des soupapes principales d'un moteur à combustion interne, en particulier pour une opération de freinage d'un moteur de décompression
CN110374707A (zh) * 2019-06-19 2019-10-25 浙江吉利控股集团有限公司 一种连续可变升程装置、发动机及汽车

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59201911A (ja) * 1983-04-28 1984-11-15 Mazda Motor Corp エンジンの弁不作動装置
JPS60116809A (ja) * 1983-11-25 1985-06-24 Mazda Motor Corp エンジンの弁不作動装置
JPH06193415A (ja) * 1992-12-24 1994-07-12 Unisia Jecs Corp 内燃機関の吸気弁制御装置
FR2724975A1 (fr) * 1994-09-27 1996-03-29 Peugeot Dispositif pour l'actionnement d'au moins une soupape de moteur a combustion interne
US5673660A (en) * 1995-04-04 1997-10-07 Chrysler Corporation Valve train for internal combustion engine
EP0814240A1 (fr) * 1996-06-11 1997-12-29 Ricardo Consulting Engineers Limited Poussoir de soupape hydraulique

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DE2825316A1 (de) * 1978-06-09 1979-12-20 Maschf Augsburg Nuernberg Ag Regelbare hydraulische ventilsteuerung fuer hubkolbenkraft- oder arbeitsmaschinen
US5829397A (en) * 1995-08-08 1998-11-03 Diesel Engine Retarders, Inc. System and method for controlling the amount of lost motion between an engine valve and a valve actuation means
US6293237B1 (en) * 1997-12-11 2001-09-25 Diesel Engine Retarders, Inc. Variable lost motion valve actuator and method

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59201911A (ja) * 1983-04-28 1984-11-15 Mazda Motor Corp エンジンの弁不作動装置
JPS60116809A (ja) * 1983-11-25 1985-06-24 Mazda Motor Corp エンジンの弁不作動装置
JPH06193415A (ja) * 1992-12-24 1994-07-12 Unisia Jecs Corp 内燃機関の吸気弁制御装置
FR2724975A1 (fr) * 1994-09-27 1996-03-29 Peugeot Dispositif pour l'actionnement d'au moins une soupape de moteur a combustion interne
US5673660A (en) * 1995-04-04 1997-10-07 Chrysler Corporation Valve train for internal combustion engine
EP0814240A1 (fr) * 1996-06-11 1997-12-29 Ricardo Consulting Engineers Limited Poussoir de soupape hydraulique

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* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 009, no. 070 (M - 367) 30 March 1985 (1985-03-30) *
PATENT ABSTRACTS OF JAPAN vol. 009, no. 272 (M - 425) 30 October 1985 (1985-10-30) *
PATENT ABSTRACTS OF JAPAN vol. 018, no. 548 (M - 1689) 19 October 1994 (1994-10-19) *

Also Published As

Publication number Publication date
EP1367231B1 (fr) 2005-04-20
US6779497B2 (en) 2004-08-24
DE50300451D1 (de) 2005-05-25
US20030209215A1 (en) 2003-11-13
DE10220692A1 (de) 2003-11-20
ES2242120T3 (es) 2005-11-01

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