EP0626035A1 - Commande de soupape pour un moteur a combustion interne. - Google Patents

Commande de soupape pour un moteur a combustion interne.

Info

Publication number
EP0626035A1
EP0626035A1 EP94902714A EP94902714A EP0626035A1 EP 0626035 A1 EP0626035 A1 EP 0626035A1 EP 94902714 A EP94902714 A EP 94902714A EP 94902714 A EP94902714 A EP 94902714A EP 0626035 A1 EP0626035 A1 EP 0626035A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
camshaft
eccentric
shaft
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
EP94902714A
Other languages
German (de)
English (en)
Other versions
EP0626035B1 (fr
Inventor
Gert Fischer
Johannes Hoehl
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0626035A1 publication Critical patent/EP0626035A1/fr
Application granted granted Critical
Publication of EP0626035B1 publication Critical patent/EP0626035B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F01L13/0015—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
    • F01L13/0021—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 rocker arm ratio
    • F01L13/0026—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 rocker arm ratio by means of an eccentric
    • 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
    • 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

Definitions

  • the invention is based on GB-PS 955 988 and relates to a valve control for changing the valve opening period when the valve lift varies within a limited range due to the system.
  • a plunger is provided as a transmission member in a guide which can be tilted by means of a control device as a function of the speed about an axis parallel to the camshaft.
  • the tappet which is provided with a flat contact track, can be tilted both in and against the direction of rotation of the camshaft, as a result of which valve stroke profiles with different valve opening periods are achieved.
  • the control device comprises an eccentrically arranged bolt which rotates with the camshaft and which is arranged with relatively stiff but elastically bendable control arms on the tappet guide cooperates.
  • the guide is connected to a flexible stop, the stop at low machine speeds allows the guide to be tipped with the tappet via the relatively unyielding control arms to reduce the valve opening period with a possible elimination of the valve overlaps.
  • the stop holds the guide with the tappet in a non-tilted position at high machine speeds, the control arms deflecting the starting, eccentrically arranged bolt in a flexurally elastic manner.
  • a disadvantage of this known valve control are the flexible control arms of the control device provided for the speed-dependent tilt control, which in a multi-cylinder internal combustion engine lead to different valve opening periods at one and the same speed over all cylinders and are therefore subject to unacceptable fluctuations in performance and exhaust gas quality.
  • a valve control for the targeted load and speed-dependent change of the valve opening angle of a gas exchange valve is known.
  • This known valve control differs from the valve control described above in that the camshaft is equipped with an eccentrically arranged driver for radially movable engagement in a radial slot of a drive wheel separate from the camshaft.
  • the drive wheel is displaced in a transverse direction relative to the camshaft, with the consequence of a non-uniform rotational speed of the camshaft coupled via the driver when the drive wheel rotates constantly.
  • This valve control which is based on the principle of constantly non-uniform rotational speeds by deliberate decaching of the components which are coupled with one another in rotation, is disadvantageously expensive to construct.
  • the object of the invention is to improve the control device for changing the valve opening periods in the case of a valve control according to the system when the valve lift varies within limits, so that exact control is achieved with little construction effort.
  • a valve control is specified in claims 2 and 3 as well as in claim 4, in which the intermediate element arranged between the control cam and the valve-side transmission element is located in one to the axis of the camshaft concentric circular arc section is movably mounted tilting segment.
  • the difference between the two configurations lies in the rigid control arm arranged relative to the valve stroke direction.
  • the rigid control arm on the tilting segment is designed to extend transversely to the valve lifting direction for the advantageous use of a cam disc or eccentric gearbox which is simple in construction for the purpose of positively controlling the preferably in a tappet the tilted arc segment concentrically mounted to the camshaft.
  • DE-A 39 20 895 also discloses an intermediate element or tilting segment which is positively controlled relative to the tappet, but which, as part of a resilient four-link chain, is controlled via a coupling by a crank mechanism and cooperates with a flat contact path of the tappet Stroke change of the tappet with simultaneous change in the valve opening period of the gas exchange valve acted upon by the tappet.
  • the force-controlled tilting segment according to the invention is part of a push-loop chain, in which, as is known, each transmission link has a rotating joint and a pushing joint.
  • a pair of joints is formed from the stroke-actuated tappet with the tilting segment guided about the axis of the camshaft via the concentric circular arc section in the tappet, the rigid, fork-like control arm with the crank disk or the eccentric being the second joint pairing forms.
  • this thrust loop chain designed in this way makes it possible to change the valve opening period primarily in the case of a kinematic system-dependent valve stroke which differs within narrow limits and a different spread.
  • the example of a tilting segment designed according to claim 4 with a rigid control arm directed in the valve stroke direction also enables the use of a rotating crank or eccentric gear for the positive control of the tilting segment.
  • the difference from the prior art according to the aforementioned DE-A 39 20 895 is the mounting of the tilting segment in the respective transmission member in a circular arc section concentric to the axis of the camshaft for the predominant change of the valve opening period.
  • a preferred embodiment of the invention shown in principle in claim 1 is described in claims 5 to 10.
  • valve control in a predetermined rotation angle assignment of the control shaft of the control device, which rotates synchronously with the camshaft, the roller arranged on the transmission member side is moved relative to the control cam acting with its direction of rotation, and in an opposite rotation angle assignment, the role becomes relative to the control cam acting against its direction of rotation controlled moves.
  • the roller in the transmission element which is driven in the same direction relative to the control cam, a valve lift curve with a large valve opening angle or a long valve opening period results, as is advantageous for a high power output of the internal combustion engine.
  • the roller in the transmission element which is driven in the opposite direction relative to the control cam, results in a valve lift curve with a small valve opening angle or short valve opening period, which results in advantageous operation, in particular at low engine speed.
  • the roller in the transmission element which can be displaced in the same direction relative to the direction of rotation of the control cam, results in a lower absolute speed for the line of contact between the control cam and the contact track of the roller compared to a stationary roller, which occurs at a constant speed of the camshaft large valve opening angle corresponds. If the roller is shifted in the opposite direction, the contour of the control cam is transmitted more quickly to the transmission element and thus to the respective gas exchange valve. A high absolute speed thus results for the contact line, which corresponds to a small valve opening angle at constant camshaft speed.
  • valve control of the above-mentioned CH-PS 390 617 corresponds kinematically to a thrust loop chain like the valve control claimed, but due to the operating point-dependent adjustment of the cam spread with unchanged opening and closing times of the respective valve only discontinuously or as required controls is influenced.
  • valve control of GB-PS 649 192 mentioned earlier enables A change in the valve opening angle of a gas exchange valve as a function of the operating point, which, however, is achieved in a kinetically deviating manner with a revolving crank loop in which two transmission members rotating about axes which are offset in parallel with one another are coupled by means of a sliding joint.
  • the roller which is controlled synchronously in the same and opposite directions relative to the control cam, is provided on a valve lever, preferably on a rocker arm.
  • the rocker arm designed according to the invention is characterized by an advantageously low construction.
  • the advantage of the low design, in particular for a cylinder head, is further promoted by the design of the push rods which move the rollers and which, by means of a fork-like design, comprise the rocker arms in the longitudinal direction for an essentially flush arrangement, at least in the basic circle phase of the control cam.
  • the inlet-side and the outlet-side roller push rods can each be driven by means of a separate control shaft.
  • Separate control shafts per se for controllable rocker arms for changing the opening time for the exhaust valve and for changing the closing time for the intake valve are known from US Pat. No. 2,880,712.
  • a valve control with a single cam follower for roller and cam actuators designed for actuating intake and exhaust valves which is advantageous in terms of small installation space and small construction expenditure, is achieved according to claim 9 in that a single cam shaft, which is equipped with an eccentric, is adjustable via a fork ⁇ -like push rods controls both the rollers of the inlet rocker arms and the rollers of the exhaust rocker arms synchronously in the same and opposite directions relative to the respective control cam of the camshaft.
  • This control arrangement can be provided particularly advantageously in the case of a cross-flow cylinder head with an ohc arrangement according to claim 10 in the region above the generally angled gas exchange outlet channels. whereby the intake ports can be optimally designed with this cylinder head.
  • FIG. 1 shows a first valve control with a tappet which is equipped with a tilting segment on the cam side
  • FIG. 2 shows a second, schematically illustrated valve control with a tilting segment modified compared to FIG. 1,
  • FIG. 3 shows a third valve control with rocker arms designed according to the invention in a perspective view
  • Figure 4 shows the valve control according to Figure 3 with a
  • FIG. 5 stroke curves for inlet and outlet valves at changed opening and closing times, achieved with one of the above. Valve controls.
  • valve control 1 denotes a valve control for a gas exchange valve, not shown, of an internal combustion engine.
  • the valve control 1 comprises a camshaft 2 with a control cam 3, which acts on a contact track 4 of a tappet 5 for opening and closing the gas exchange valve, not shown.
  • the contact track 4 is formed on a circular arc in the tappet 5 in a circular arc concentric with the camshaft 2.
  • Section 5 'tilting-mounted tilting segment 6, which is part of a control device 7 for changing the valve opening period with a system-related essentially constant stroke of the gas exchange valve.
  • a rigid control arm 8 is arranged transversely to the valve stroke direction, which is in a positively controlled or desmodromic drive connection via two fork-like, free end sections 9 and 10 with a cam disk 12 designed as an eccentric 11.
  • the eccentric 11 is connected to a separate shaft 13 in a rotationally fixed connection, the shaft 13 being driven continuously synchronously by an output gear 15 of the camshaft 2 via a drive gear 14.
  • the eccentric shaft 13 is connected via an arbitrary drive device, not shown, in a couplable connection such that the phase position of the eccentric 11 is controlled relative to the camshaft 2 for the purpose of changing the valve opening period in each case by approximately 180 ° in a direction from I to II and finally can be changed progressively from II to I.
  • the tilting control of the tilting segment 6, which serves to change the valve opening periods in the case of valve lift curves with a system-dependent change in valve lift within limits, is superimposed on the tilting movement forced from the valve lift of the tappet 5 and the control arm 8 supported on the control device side.
  • the extent of the superimposed tilting movement is essentially determined from the lever distance of the control arm 8 and the stroke of the eccentric 11, which can also be designed to be stroke-adjustable relative to the shaft 13 for further different valve opening periods.
  • a control cam 17 of a camshaft 18 acts with the contact track 19 in a transmission member 20 - tappet or valve lever - via a Camshaft 18 concentric circular arc section 21 ge tilted segment 22 together.
  • the tilting segment 22 is equipped with a rigid control arm 23 which is approximately parallel to the transmission member 20 in the valve stroke direction and on which a push rod 24 of a crank or eccentric gear 25 adjustable in angle of rotation and adjustable in synchronism with the camshaft 18 is articulated attacks.
  • a valve control 26 shown in FIGS. 3 and 4 comprises a common camshaft 29 with an intake control cam 30 and an exhaust control cam 31 for actuating an intake valve 27 and an exhaust valve 28, each of which has a roller 32 with a contact track 32 'act on a corresponding rocker arm 33.
  • Each of the rollers 32 is arranged in the respective drag lever 33 between webs 34 which have circular arc sections 35 which are concentric with the axis of the camshaft 29. These circular arc sections 35 serve as guide tracks for support bolts 36 of the rollers 32.
  • Arms 37 of a fork-shaped push rod 38 engage on each support bolt 36 on both ends of the respective rocker arm 33.
  • Each of the push rods 38 is in drive connection with an eccentric 39 of a shaft 40 of a control device 41 which is driven synchronously with the camshaft 29 and is adjustable in angle of rotation.
  • a single eccentric shaft 40 serves to control the rollers 32 in the rocker arms 33 on the inlet and outlet side.
  • the only eccentric shaft 40 of the control device 41 is provided with an only indicated cross-flow cylinder head 42 with ohc
  • the arrangement is preferably arranged on the outlet side above the usually strongly curved gas exchange outlet channels 43. This arrangement, which requires little installation space, advantageously makes possible approximately in the basic circle phase of the respective control cam 30, 31 Aligned arrangement of rocker arm 33 and push rod 38.
  • This assignment can be used advantageously to the effect that a reversal point of the roller 32 in an end region of the transmission link or rocker arm-side circular arc sections 35 from the same to the opposite drive and vice versa and one of the the two extreme positions of the eccentric 39 controlling the push rod 38 are arranged on a straight line essentially intersecting the axis of the eccentric shaft 40.
  • the respective control cam 30, 31 is in a transverse direction to the respective straight line.
  • This arrangement has a kinetically favorable effect on a shaft 40 with eccentrics provided for many gas exchange valves of a multi-valve combustion chamber and / or a multi-cylinder internal combustion engine, with the result that, by balancing oppositely acting torques in total, an advantageously balanced overall torque on the eccentric shaft 40 is reached.
  • This balanced total torque is of essential importance for a phase position controllable driving device 44 assigned to the eccentric shaft 40.
  • the eccentric shaft 40 is driven synchronously via a gear transmission 45 to the camshaft 29.
  • the driving device 44 is assigned to the gear 46 on the eccentric shaft 40.
  • the driving device 44 comprises two stop supports 47 and 48, which are connected in a rotationally fixed manner to the eccentric shaft 40 and are arranged at a fixed axial distance, each with a driving stop 49 and 50.
  • one on the eccentric shaft 40 between the Impact carriers 47 and 48 - gear 46 is at the same time the stop carrier 47 - non-rotatably but axially displaceably provided arm 51 for entrainment via one of the predetermined rotation or phase angles - preferably offset by approximately 180 ° Stops 49 and 50.
  • the arm 51 For adjusting the angle of rotation of the eccentric shaft 40 relative to the camshaft 29, the arm 51 is brought out of engagement with one of the drive-fixed stops 49, 50 by means of a controlled, axial displacement and then the arm 51 which is not driven in the direction of rotation is moved from the other stop 50 or 49 to Rotational entrainment.
  • This small, light and simply constructed entrainment device 44 results in the advantageously selected position of the eccentric shaft 40 relative to the rollers 32 which are displaced synchronously and in opposite directions relative to the rotating control cams 30, 31 in the rocker arms 33 along circular arc sections 35.
  • valve lift curves shown with solid lines correspond to the lift profile of the respective control cam.
  • valve control according to the invention can, if required, be combined with a separate device for specifically changing the valve stroke and / or for specifically changing the spread. This opens up the possibility of being able to optimally adapt a valve control to a respective operating point of the internal combustion engine by means of independent control of the respective device.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Pour une commande de soupape (26), présentée sur la fig. 3, d'un moteur à combustion interne, dans laquelle un arbre à came (29) muni d'une came de commande (30, 31) agit sur une soupage (29) par l'intermédiaire d'un élément de transmission (33) dont la voie de contact (32') située côté came peut être modifiée dans sa position relative par rapport à la came de commande (39, 31) au moyen d'un dispositif de commande (41) afin de modifier le temps d'ouverture de la soupape pour une course de soupape sensiblement constante inhérente au système, l'invention suggère, afin de parvenir à une commande précise, que la voie de contact (32') soit réalisée sur un galet (32) monté à commande forcée par rapport à la tige de culbuteur (33) en synchronisme avec l'arbre à came (29), en tant qu'élément intermédiaire entre la came de commande (30, 31) et la tige de culbuteur (33).
EP94902714A 1992-12-13 1993-12-08 Commande de soupape pour un moteur a combustion interne Expired - Lifetime EP0626035B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4242060 1992-12-13
DE4242060 1992-12-13
PCT/EP1993/003451 WO1994013935A1 (fr) 1992-12-13 1993-12-08 Commande de soupape pour un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0626035A1 true EP0626035A1 (fr) 1994-11-30
EP0626035B1 EP0626035B1 (fr) 1997-08-13

Family

ID=6475170

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94902714A Expired - Lifetime EP0626035B1 (fr) 1992-12-13 1993-12-08 Commande de soupape pour un moteur a combustion interne

Country Status (3)

Country Link
EP (1) EP0626035B1 (fr)
DE (1) DE59307123D1 (fr)
WO (1) WO1994013935A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0685633A1 (fr) * 1994-05-31 1995-12-06 Bayerische Motoren Werke Aktiengesellschaft Commande de soupape avec dispositif pour varier l'instant d'ouverture et de fermeture d'une soupape à levée, particulièrement pour moteurs à combustion interne

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0717174A1 (fr) * 1994-12-12 1996-06-19 Isuzu Motors Limited Système de commande de soupape pour moteur à combustion interne
DE19537377A1 (de) * 1995-10-06 1997-04-10 Bayerische Motoren Werke Ag Vorrichtung zur Veränderung des Hubverlaufes von Brennkraftmaschinen-Ventilen
US5937809A (en) * 1997-03-20 1999-08-17 General Motors Corporation Variable valve timing mechanisms
DE19825307A1 (de) 1998-06-05 1999-12-09 Bayerische Motoren Werke Ag Ventilsteuerung für eine Brennkraftmaschine
JP2001164911A (ja) * 1999-12-10 2001-06-19 Yamaha Motor Co Ltd ４サイクルエンジンの動弁機構
DE102011001612B4 (de) * 2011-03-29 2013-02-28 Pierburg Gmbh Vorrichtung zur diskreten Phasenverschiebung
CN112523875B (zh) * 2020-12-01 2022-08-12 广西玉柴机器股份有限公司 一种船用发动机越控功能的控制方法

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Publication number Priority date Publication date Assignee Title
US2266077A (en) * 1938-10-03 1941-12-16 Henry A Roan Internal combustion engine
US2880712A (en) * 1958-07-03 1959-04-07 Henry A Roan Variable valve timing for overhead cam engines
FR2500528B1 (fr) * 1981-02-20 1985-10-11 Ferrer Jean Mecanisme de commande des soupapes d'admission, d'un moteur a combustion interne, pour un temps d'admission prolonge
US4469056A (en) * 1983-02-22 1984-09-04 Tourtelot Jr Edward M Dual follower variable valve timing mechanism
US4530318A (en) * 1984-01-20 1985-07-23 Carol M. Semple Intake and exhaust valve system for internal combustion engine
DE3519319A1 (de) * 1985-05-30 1986-12-04 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Variable ventilsteuerung fuer eine hubkolben-brennkraftmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9413935A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0685633A1 (fr) * 1994-05-31 1995-12-06 Bayerische Motoren Werke Aktiengesellschaft Commande de soupape avec dispositif pour varier l'instant d'ouverture et de fermeture d'une soupape à levée, particulièrement pour moteurs à combustion interne

Also Published As

Publication number Publication date
WO1994013935A1 (fr) 1994-06-23
DE59307123D1 (de) 1997-09-18
EP0626035B1 (fr) 1997-08-13

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