EP0179990A2 - Procédé pour commander la distribution variable de soupape pour un moteur à combustion interne - Google Patents

Procédé pour commander la distribution variable de soupape pour un moteur à combustion interne Download PDF

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Publication number
EP0179990A2
EP0179990A2 EP85109787A EP85109787A EP0179990A2 EP 0179990 A2 EP0179990 A2 EP 0179990A2 EP 85109787 A EP85109787 A EP 85109787A EP 85109787 A EP85109787 A EP 85109787A EP 0179990 A2 EP0179990 A2 EP 0179990A2
Authority
EP
European Patent Office
Prior art keywords
valve
adjuster
rocker arm
engine
pivot
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.)
Withdrawn
Application number
EP85109787A
Other languages
German (de)
English (en)
Other versions
EP0179990A3 (fr
Inventor
Russell J. Wakeman
Jack R. Phipps
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.)
Allied Corp
Original Assignee
Allied Corp
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 Allied Corp filed Critical Allied Corp
Publication of EP0179990A2 publication Critical patent/EP0179990A2/fr
Publication of EP0179990A3 publication Critical patent/EP0179990A3/fr
Withdrawn legal-status Critical Current

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    • 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
    • F01L31/00—Valve drive, valve adjustment during operation, or other valve control, not provided for in groups F01L15/00 - F01L29/00
    • 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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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

Definitions

  • This invention relates to engine control systems in general and more particularly to electrohydraulic control systems for controlling the timing of the intake and exhaust valves in internal combustion engines.
  • valve timing It has been long recognized by engine builders and more particularly by specialists in high performance engines that control of valve timing will yield desired engine operation results.
  • the ideal timing of intake and exhaust valves at idle conditions, at normal load range conditions and at high performance conditions is very different. Since valves are controlled by cams it is necessary to compromise the timing to suit a particular purpose. In production engines, valve timing is a compromise leaning towards the normal load or speed ranges to the detriment of the idle range and the high performance range. Likewise in high performance engines the timing is adjusted toward the high performance demands of the engine and therefore at the idle and normal load ranges valve timing is not optimal.
  • I disclosed an engine valve timing control system using the engine oil supply to operate the hydraulic valve adjusters.
  • the system is a microprocessor based control system wherein various engine sensors sense the engine conditions and the microprocessor in response to the sensed engine conditions addresses a memory unit containing a map of engine conditions versus valve opening times. From the memory unit a signal is supplied to a particular timer unit for a given cylinder. The timer, operating in conjunction with a known position of the piston in the cylinder will operate electrohydraulic solenoid valves for directing and maintaining a predetermined amount of oil in an associated hydraulic valve adjuster.
  • the electronic control system controlled the flow of the hydraulic oil supply out of the hydraulic valve adjusters.
  • the camshaft operating on the rocker arm with the rocker arm pivoting on the valve stem caused the hydraulic valve adjuster to collapse forcing the oil out of the hydraulic valve adjuster until the desired operating time was reached.
  • a solenoid controlled valve closed preventing the flow of oil thereby forming a rigid oil link.
  • the camshaft continuing rotating, shifted the pivot point of the rocker arm from the valve stem to the hydraulic valve adjuster causing the valve to open.
  • the longitudinal axis of the hydraulic valve adjuster and the longitudinal axis of the valve stem are parallel. In conventional engines, the effects of hydraulic valve adjuster height on the valve motions causes changes in valve height opening.
  • valve timing control is achieved by inclining the longitudinal axis of the hydraulic valve adjuster by a predetermined angle, 0, relative to the axis of the valve stem.
  • the pivot point of the rocker arm changes as the hydraulic valve adjuster is collapsed thereby changing the ratio of the arm length from the pivot point to point on the cam applying force to the rocker arm.
  • a method for variable valve timing in an internal combustion engine having at least one timing cam controlling a rocker arm for at least one engine valve comprises the steps of determining the rocker arm ratio as a function of the distances between the centerline of the timing cam and the pivot point of the rocker arm and the longitudinal axis of the valve. The next step providing hydraulic valve adjusters for controlling the pivot point of the rocker arms. Then positioning the longitudinal axis of the hydraulic valve adjuster at an angle intersecting the longitudinal axis of the valve.
  • the step of adjusting the height of the valve adjuster to move the pivot point of the rocker arm along the longitudinal axis of the hydraulic valve adjuster thereby changing the rocker arm ratio and then rotating the timing cam for setting the rocker arm pivot on the hydraulic valve adjuster.
  • Finally opening the valve a predetermined height as a function of the location of the pivot point on the hydraulic valve adjuster.
  • FIGURE 1 illustrates the conventional parallel relationship of the centerline 10 or longitudinal axis of the hydraulic valve adjuster 12 to the longitudinal axis 14 of the valve means 16.
  • the valve means 16 has a valve member 18, a valve stem 20, a keeper block 22, and a spring 24 bearing against the keeper block for biasing the valve member 18 closed on a valve seat 26.
  • the height of the valve member 18 opening or lift and the duration of valve opening is inversely proportional to the distance (d) of the hydraulic valve adjuster 12 collapse.
  • FIGURE 2 is a graphic representation of the change in valve member 18 opening on the ordinate with degrees of rotation of the camshaft 28 on the abscissa.
  • the slope at the beginning and the end of the curve 30 is smooth indicating that the valve means 16 follows the cam profile 32 and the closing of the valve means 16 on the valve seat 26 is during the period of slow travel of the valve means 16.
  • valve seat The portion of all curves below the horizontal line, called “valve seat”, are not actual conditions but illustrate the opening and closing of the valve member 18 on the valve seat 26 during the rise and fall, respectively, of the cam 32.
  • the rocker arm 36 ratio is not changed but the valve means 16 lift and duration are variable.
  • FIGURE 3 illustrates the improvement to the above system wherein the pivot point of the rocker arm 36 may be constantly variable to achieve desired valve operations at various engine speeds.
  • the longitudinal axis of the hydraulic valve adjuster 10 is in a non-parallel relationship to the longitudinal axis of the valve means 16.
  • the rocker arm ratio (R r ) is defined as where:
  • valve lift is not controlled but is a function of opening time. The earlier the opening, the higher the valve lift.
  • the rocker arm 36 ratio is determined as it varies from one extreme when the adjuster is extended: or to when the rocker arm adjuster is collapsed or where:
  • hydraulic valve adjusters 12 are provided for controlling the pivot point of the rocker arm 36.
  • ⁇ intersecting the centerline or longitudinal axis of the valve means 16
  • rocker arm 36 ratio (Rr ) can be varied as a function of:
  • the rotation of the cam 32 sets the pivot point and the amount of lift can be selected. If the inclination angle ⁇ in FIGURE 2 is increased, the rocker arm 36 ratio is decreased as the hydraulic valve adjuster 12 collapses and the dimension b c is increased or lengthened, the lift or height of the valve opening decreases. As stated in the previous patent application, as the timing cam 32 rotates, the rocker arm 36 pivot bears against the hydraulic valve adjuster 12 and as long as the control solenoid 40 is open, the fluid flows out of the adjuster 12 and the adjuster collapses until the hydraulic flow path is closed. It is this movement that determines the pivot point.
  • the reduction in rocker arm 36 ratio can be used to minimize the amount of hydraulic valve adjuster 36 stroke necessary. Either effect adds significantly to the flexibility of a variable valve timing system.
  • the second strategy is one that the engine builder determines that a fixed change in the valve means 16 opening is desired for two different engine operations.
  • the largest valve lift is typically for high speed or heavy load and the smallest or second valve lift is at idle where the effects of valve timing control will make up for throttle body loses.
  • d is either "0" (zero) or "X”.
  • the size of hydraulic valve adjuster 12, hence the amount and control of hydraulic oil, is smaller than in the first strategy.
  • FIGURE 4 graphically illustrates the effects of variable rocker arm 36 ratios which can and will be achieved by a suitable selection of the angle 0. If the angle -8- equals zero, then the system of the prior identified patent application is applicable, however by having the angle-e-equal a finite number of degrees, the rocker arm 36 ratio is reduced as the hydraulic valve adjuster 12 collapses.
  • FIGURE 5 Another embodiment of variable valve timing system that also effects valve lift is shown in FIGURE 5 where the hydraulic valve adjuster is replaced by a linear solenoid 42 and a lever means 44.
  • One end of the rocker arm 46 bears on the end of the valve stem 20, a portion 48 adapted to follow the timing cam 32, and a pivot portion 50 or lever pivot, which is a moveable pivot is located by another pivoting lever 52.
  • the rocker arm 46 has a designed shape portion 48 to accomplish the amount of valve lift with the time of opening.
  • the moveable pivot 50 operates to change the rocker arm 46 ratio and is biased by means such as a spring 54 to return to a home position.
  • the solenoid 42 being a linear solenoid, moves its actuator or plunger 56 a distance proportional to the time electric power is applied to the solenoid.
  • the bias means 54 restores or returns the plunger 56 and therefore the rocker arm 46 to its home position.
  • This system does not require hydraulic fluid but does require large power linear solenoids.
  • Electric power is supplied to the linear actuator 42 by means of an electronic control unit 58 which is adapted to generate valve timing signals in response to a plurality of engine operating signals 60.
  • the signals generated for this embodiment are similar to those generated for the embodiment shown in FIGURE 3 in that in each, the timing of the signal is proportional to the desired valve timing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP85109787A 1984-09-28 1985-08-03 Procédé pour commander la distribution variable de soupape pour un moteur à combustion interne Withdrawn EP0179990A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US65605384A 1984-09-28 1984-09-28
US656053 1984-09-28

Publications (2)

Publication Number Publication Date
EP0179990A2 true EP0179990A2 (fr) 1986-05-07
EP0179990A3 EP0179990A3 (fr) 1987-02-25

Family

ID=24631434

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109787A Withdrawn EP0179990A3 (fr) 1984-09-28 1985-08-03 Procédé pour commander la distribution variable de soupape pour un moteur à combustion interne

Country Status (5)

Country Link
EP (1) EP0179990A3 (fr)
JP (1) JPS6185517A (fr)
KR (1) KR860002635A (fr)
AU (1) AU4584085A (fr)
ES (1) ES8703574A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0286389A2 (fr) * 1987-04-07 1988-10-12 The British Internal Combustion Engine Research Institute Limited Dispositif pour régler la distribution d'une soupape
DE4211631A1 (de) * 1992-04-07 1993-04-08 Bayerische Motoren Werke Ag Ventiltrieb mit einem laengsverschiebbaren spielausgleichselement
GB2273956A (en) * 1993-01-05 1994-07-06 Peter David Stewart I.c. engine with variable valve lift.
EP0367552B1 (fr) * 1988-10-31 1994-08-31 Isuzu Motors Limited Dispositif de commande de soupape pour moteur à combustion interne
WO2004067924A1 (fr) * 2003-01-28 2004-08-12 Fev Motorentechnik Gmbh Entrainement mecanique de soupape entierement variable destine a moteur a combustion interne a piston alternatif a equilibre de jeu de soupapes reglable
GB2512925A (en) * 2013-04-11 2014-10-15 Daimler Ag Valve train for an internal combustion engine
DE102017205151A1 (de) 2017-03-27 2018-09-27 Mahle International Gmbh Ventiltrieb für eine Brennkraftmaschine
DE102017205155A1 (de) 2017-03-27 2018-09-27 Mahle International Gmbh Ventiltrieb für eine Brennkraftmaschine
CN112189081A (zh) * 2018-06-13 2021-01-05 马勒国际有限公司 具有切换装置的气门驱动装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0365812U (fr) * 1989-10-31 1991-06-26
JP5035866B2 (ja) * 2005-10-04 2012-09-26 ヤンマー株式会社 作業車両における動力伝達装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB213894A (en) * 1923-04-05 1924-09-18 Henry Farman Improvements relating to the regulation of internal-combustion engines for aircraft
US2763250A (en) * 1952-08-29 1956-09-18 Daimler Benz Ag Valve actuating mechanism for internal combustion engines
GB2053350A (en) * 1979-06-14 1981-02-04 Nissan Motor Ic engine valve gear
US4258671A (en) * 1978-03-13 1981-03-31 Toyota Jidosha Kogyo Kabushiki Kaisha Variable valve lift mechanism used in an internal combustion engine
EP0156996A1 (fr) * 1984-01-30 1985-10-09 Allied Corporation Système de contrôle pour le timonerie des soupapes d'un moteur

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB213894A (en) * 1923-04-05 1924-09-18 Henry Farman Improvements relating to the regulation of internal-combustion engines for aircraft
US2763250A (en) * 1952-08-29 1956-09-18 Daimler Benz Ag Valve actuating mechanism for internal combustion engines
US4258671A (en) * 1978-03-13 1981-03-31 Toyota Jidosha Kogyo Kabushiki Kaisha Variable valve lift mechanism used in an internal combustion engine
GB2053350A (en) * 1979-06-14 1981-02-04 Nissan Motor Ic engine valve gear
EP0156996A1 (fr) * 1984-01-30 1985-10-09 Allied Corporation Système de contrôle pour le timonerie des soupapes d'un moteur

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0286389A2 (fr) * 1987-04-07 1988-10-12 The British Internal Combustion Engine Research Institute Limited Dispositif pour régler la distribution d'une soupape
EP0286389A3 (fr) * 1987-04-07 1989-02-15 The British Internal Combustion Engine Research Institute Limited Dispositif pour régler la distribution d'une soupape
US4883026A (en) * 1987-04-07 1989-11-28 British Internal Combustion Engine Research Institute, Ltd. Means for adjusting the timing of a valve
EP0367552B1 (fr) * 1988-10-31 1994-08-31 Isuzu Motors Limited Dispositif de commande de soupape pour moteur à combustion interne
DE4211631A1 (de) * 1992-04-07 1993-04-08 Bayerische Motoren Werke Ag Ventiltrieb mit einem laengsverschiebbaren spielausgleichselement
GB2273956A (en) * 1993-01-05 1994-07-06 Peter David Stewart I.c. engine with variable valve lift.
GB2273956B (en) * 1993-01-05 1996-04-17 Peter David Stewart An internal combustion engine incorporating variable valve lift
CN100460633C (zh) * 2003-01-28 2009-02-11 Fev电机技术有限公司 供具有可调气门间隙补偿装置的活塞内燃机用的全可变机械气门驱动机构
WO2004067924A1 (fr) * 2003-01-28 2004-08-12 Fev Motorentechnik Gmbh Entrainement mecanique de soupape entierement variable destine a moteur a combustion interne a piston alternatif a equilibre de jeu de soupapes reglable
GB2512925A (en) * 2013-04-11 2014-10-15 Daimler Ag Valve train for an internal combustion engine
DE102017205151A1 (de) 2017-03-27 2018-09-27 Mahle International Gmbh Ventiltrieb für eine Brennkraftmaschine
DE102017205155A1 (de) 2017-03-27 2018-09-27 Mahle International Gmbh Ventiltrieb für eine Brennkraftmaschine
US10428702B2 (en) 2017-03-27 2019-10-01 Mahle International Gmbh Valve drive for an internal combustion engine
US10428701B2 (en) 2017-03-27 2019-10-01 Mahle International Gmbh Valve drive for an internal combustion engine
CN112189081A (zh) * 2018-06-13 2021-01-05 马勒国际有限公司 具有切换装置的气门驱动装置
US11236646B2 (en) 2018-06-13 2022-02-01 Mahle International Gmbh Valve drive device with switchover device
CN112189081B (zh) * 2018-06-13 2022-03-25 马勒国际有限公司 具有切换装置的气门驱动装置

Also Published As

Publication number Publication date
EP0179990A3 (fr) 1987-02-25
ES547396A0 (es) 1987-02-16
ES8703574A1 (es) 1987-02-16
JPS6185517A (ja) 1986-05-01
KR860002635A (ko) 1986-04-28
AU4584085A (en) 1986-04-10

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