EP0807206A1 - Moteur a combustion interne - Google Patents

Moteur a combustion interne

Info

Publication number
EP0807206A1
EP0807206A1 EP96900280A EP96900280A EP0807206A1 EP 0807206 A1 EP0807206 A1 EP 0807206A1 EP 96900280 A EP96900280 A EP 96900280A EP 96900280 A EP96900280 A EP 96900280A EP 0807206 A1 EP0807206 A1 EP 0807206A1
Authority
EP
European Patent Office
Prior art keywords
eccentric
camshaft
cam
internal combustion
combustion engine
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
EP96900280A
Other languages
German (de)
English (en)
Other versions
EP0807206B1 (fr
Inventor
Erwin Korostenski
Armin Bertsch
Reiner Walter
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0807206A1 publication Critical patent/EP0807206A1/fr
Application granted granted Critical
Publication of EP0807206B1 publication Critical patent/EP0807206B1/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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive

Definitions

  • the invention relates to an internal combustion engine in which the rotational speed of a cam for gas exchange control can be changed cyclically by an intermediate member being displaceable in a plane perpendicular to the axis of rotation of a camshaft and being rotatable in any position within this plane.
  • Such a rotary drive arrangement is preferably used to drive cams for controlling an intake or exhaust valve of an internal combustion engine.
  • the rotary drive arrangement causes the rotation of the cam to be changed cyclically by an average speed at a constant speed of the internal combustion engine.
  • the degree of change i.e. the amount of the temporary increase in the angular velocity and the temporary decrease in the angular velocity of the
  • Cam and the phase of these changes depend on the position that an intermediate link is in relation to a drive shaft. If the intermediate link is concentric with respect to the drive shaft, the cam rotates synchronously with the drive shaft. The further the intermediate member is displaced from this concentric position in the radial direction, the greater the cyclical change in speed, the phase position of the Direction of the displacement of the intermediate link and the respective position of the cam depends.
  • the object of the invention is to carry out such an internal combustion engine so that the mechanism for causing the cyclical change in the rotational speed of the cam is compact, inexpensive and easy to manufacture, enables rigid mounting of the component and can be actuated by simple control means.
  • the invention in which two separate outer eccentrics are mounted on a common inner eccentric, is particularly suitable for an internal combustion engine with a camshaft, which has both intake and
  • Exhaust valves drives. This enables a particularly compact construction to be achieved.
  • the control and rotation of the inner eccentric and the two outer eccentrics can take place via corresponding sprockets, the outer eccentrics can be controlled either separately or together.
  • Fig. 1 is an exploded perspective
  • Fig. 3 is a section along the line A-A in Fig. 2,
  • Fig. 4a is a sectional view of an embodiment of the invention.
  • 4b shows the relationship between the actual valve lift curves caused by the cyclical change in speed of the cams and the position of the eccentrics.
  • a rotary drive arrangement which generates a cyclically variable cam movement has a shaft 1 with a central axis 5, which corresponds to this rotary drive arrangement in the embodiment of a drive shaft 1 shown in FIGS. 1 to 3.
  • An inner eccentric 30 is mounted on the shaft 1, and a needle bearing can be used for the storage. As shown in FIG. 2, the inner eccentric 30 can be secured against running to the left in FIG. 2 by means of a thrust washer 38 and a snap ring 39.
  • the inner eccentric 30 has a base body 31 and an eccentric seat 32, through which a bore 33 for receiving the shaft 1 runs.
  • the base body 31 has a circular outer contour 37, the central axis of which coincides with the central axis 5 of the shaft 1, which is also the axis of rotation.
  • the outer contour 35 of the eccentric seat 32 has a central axis which is offset by a first eccentricity e ⁇ with respect to the central axis of the bore 33 and thus with respect to the axis of rotation 5.
  • An outer eccentric 40 is rotatably mounted on the outer contour 35.
  • the outer eccentric 40 has a bore 41 which serves to receive the outer contour 35 of the eccentric seat 32 of the inner eccentric 30.
  • the outer contour 45 of the outer eccentric 40 is offset from the central axis of the bore 41 by a second eccentricity e 2 .
  • the eccentricities e-_ and e 7 can be chosen freely, but are preferably the same in amount.
  • An inner eccentric ring gear 34 is connected in a rotationally fixed manner to the outer contour 37 of the inner eccentric 30.
  • Outer eccentric ring gear 44 has a nose 43 (see FIG. 2) which engages in a groove 46 of the outer eccentric 40.
  • Rotary drive means (not shown) for controlling the respective rotational position of the inner eccentric 30 and the
  • Outer eccentrics 40 can engage in the inner eccentric ring gear 34 and the outer eccentric ring gear 44. If, for example, two stepper motors are selected as the control means, the rotational positions of the inner eccentric 30 and the outer eccentric 40 can be set separately and independently of one another, so that the outer contour
  • Intermediate member 4 rotatably mounted.
  • This intermediate member 4 has a first sliding guide 6 and a second sliding guide 7, which are each suitable for receiving a sliding block 13.
  • a first rotating body 2 is non-rotatably connected to the drive shaft 1 and has a thrust collar 2a.
  • a second rotating body 3 designed as a gear wheel is rotatably mounted on the first rotating body 2.
  • the first rotating body 2 has a bore 11 into which a first transmission element 8 designed as a pin is inserted. This pin 8 transmits the rotation of the first rotating body 2 to the intermediate member 4 via one of the sliding blocks 13 and the first sliding guide 6.
  • the second rotating body 3 has a bore 12, into which a second designed as a pin
  • Transmission element 9 is introduced.
  • the rotation of the intermediate member 4 is transmitted to the second rotating body 3 via the second sliding guide 7 and the other of the two sliding blocks 13 and the pin 9.
  • the outer eccentric ring gear 44 can be supported axially via the outer eccentric 40, the intermediate member 4 and the second rotating body 3 against the collar 2a.
  • the collar 2a of the first rotary body 2 thus has the effect that the entire rotary drive arrangement is secured against a shift to the right in FIG. 2.
  • the second rotating body 3 is designed as a gearwheel which engages with a cam gearwheel 22, so that the rotation of the second rotating body 3 is transmitted to the camshaft 21 and the cam 20 connected to it in a rotationally fixed manner.
  • the intermediate member 4 is in a position in which its central or rotational axis coincides with the central or rotational axis 5 of the drive shaft 1, the second rotary body 3 and thus the cam 20 rotate synchronously with the drive shaft 1 position is then achieved when the eccentricity e j _ and e 2 are their equal in magnitude and of the inner eccentric 30 and outer eccentric 40 of the take such a position to each other, that the two eccentricities e ⁇ and e 2 face each other diametrically.
  • a complete revolution of the drive shaft 1 still has a complete revolution of the second
  • Rotary body 3 and the cam 20 result, in the course of this entire revolution, however, there is a temporary increase in the rotational speed and a temporary decrease in the rotational speed of the second rotary body 3 and thus the cam 20.
  • the extent of this rotational speed increase or rotational speed reduction depends on that Offset of the axis of rotation of the intermediate member 4 from the central axis 5 of the drive shaft 1. The direction of this offset determines the phase position of the respective increase or decrease in rotational speed with respect to the position of the cam 20.
  • FIG. 4a shows an embodiment of the invention. This differs from the rotary drive arrangement explained above in that on a common
  • Inner eccentric 30 two outer eccentrics 40A, 40B are arranged.
  • the inner eccentric 30 can be rotated via an inner eccentric ring gear 34, while the outer eccentrics 40A, 40B can be controlled separately or together via corresponding outer eccentric ring gears 44A, 44B.
  • An intermediate member 4 is mounted on each of the two external eccentrics 40A, 40B. Another difference is that the shaft extending through the inner eccentric is the camshaft of the internal combustion engine and that the rotation of each intermediate member 4 is transmitted directly to a cam, which in turn is rotatably mounted directly on the camshaft.
  • cams can be either two intake cams or two exhaust cams of a cylinder, which can be varied simultaneously or independently of one another with regard to their rotational speed, but two non-identical cams, ie an intake cam and an exhaust cam, can also be driven. This makes it possible to influence an inlet and an outlet valve together in an internal combustion engine with only one camshaft using a common inner eccentric 30.
  • the cyclical change in the rotational speed results from the fact that, due to the axial offset of the central axes of rotation of the camshaft and the intermediate member, depending on the angular position, different driving radii r occur between the camshaft and the intermediate member on the one hand and the intermediate member and the cam on the other hand.
  • the condition that the tangential speed component v tan must be constant at a constant rotational speed W j ⁇ also applies because the distance r ⁇ of this point of engagement from the axis of rotation of the camshaft always remains constant.
  • the intermediate link and thus also the cam rotates once faster and once slower than the camshaft when the camshaft is rotated fully.
  • the lead or lag of the cam with respect to the camshaft is zero.
  • the output valve lift curve intersect, that is, the valve lift curve that is concentric Adjusting the position of the intermediate link, and the modified valve lift curve, ie the valve lift curve which occurs at the respective axis offset between the axis of rotation of the intermediate link and the axis of rotation of the camshaft.
  • Fig. 4b shows the valve lift curves in the representation customary in the field of internal combustion engines, where TDC is the top dead center of the piston, AM is the distance between the center of the outlet and TDC, i.e. the outlet spread, and EM the distance between the middle of the inlet and TDC, i.e. is the inlet spread.
  • the phase angle ⁇ shown in Fig. 4b is the angle between the maximum of the modified cam speed, i.e. the intersection of the respective output valve lift curve with the modified valve lift curve, and the
  • the value of the phase angle * f IN of the intake cam IN is preferably positive and the value of the phase angle ⁇ > E ⁇ of the exhaust cam EX is preferably negative.
  • phase angle is determined by the choice of the direction of displacement of the eccentricity in connection with the respective position of the cam tip relative to the valve actuating element, for example one
  • FIG. 4b Such a configuration is shown schematically in FIG. 4b, the representation under I relating to the inlet cam and the representation under II relating to the outlet cam.
  • the center white circle represents the camshaft, the black area the inner eccentric and the hatched area the outer eccentric.
  • the eccentricity e j _ runs of Exzentersitzes for the intake cam IN of the common inner eccentric element seen from the axis of rotation of the camshaft from about 45 degrees to the left downward and the eccentricity e 2 of the outer eccentric 40B runs exactly in the opposite direction , so that in this starting position the resulting eccentricity e for the intermediate member of the inlet cam IN is zero.
  • Exhaust cam EX of the common inner eccentric extends from the axis of rotation of the camshaft approximately 45 ° to the top left and the eccentricity e 2 of the outer eccentric 40A runs exactly in the opposite direction, so that in this starting position the resulting eccentricity e for the intermediate member of the exhaust cam EX also is zero.
  • the angles> IN and ⁇ E ⁇ therefore have a different sign.

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)

Abstract

L'invention concerne un moteur à combustion interne dans lequel la vitesse de rotation d'une came de commande peut être modifiée de manière cyclique pour la commande de l'échange gazeux, qui comprend: un arbre à came; une came montée rotative sur l'arbre à came; un élément intermédiaire (4) pouvant être déplacé dans un plan perpendiculaire à l'arbre à came et pouvant tourner dans ce plan, quelle que soit la position et qui comprend un premier guide à glissement et un second guide à glissement; un premier élément de transmission qui relie l'arbre à came au premier guide à glissement afin de transmettre le mouvement rotatif de l'arbre à came à l'élément intermédiaire (4); et un second élément de transmission qui relie la came au second guide à glissement afin de transmettre le mouvement rotatif de l'élément intermédiaire (4) à la came, de manière à ce que la came tourne de manière cyclique par rapport à l'arbre à came pendant une rotation de ce dernier, si l'axe de rotation de l'élément intermédiaire (4) est décalé par rapport à l'axe de rotation de l'arbre à came; et également, un excentrique intérieur (30) monté rotatif sur l'arbre à came, ainsi qu'un excentrique extérieur (40) monté rotatif sur l'excentrique intérieur (30), l'élément intermédiaire (4) étant monté rotatif sur l'excentrique extérieur (40) et deux excentriques extérieurs (40A, 40B) étant disposés sur un excentrique intérieur (30).
EP96900280A 1995-01-30 1996-01-17 Moteur a combustion interne Expired - Lifetime EP0807206B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19502834 1995-01-30
DE19502834A DE19502834A1 (de) 1995-01-30 1995-01-30 Anordnung zur Lagerung eines Bauteils
PCT/DE1996/000056 WO1996023964A1 (fr) 1995-01-30 1996-01-17 Moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP0807206A1 true EP0807206A1 (fr) 1997-11-19
EP0807206B1 EP0807206B1 (fr) 2000-03-29

Family

ID=7752638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900280A Expired - Lifetime EP0807206B1 (fr) 1995-01-30 1996-01-17 Moteur a combustion interne

Country Status (4)

Country Link
EP (1) EP0807206B1 (fr)
AU (1) AU4384896A (fr)
DE (2) DE19502834A1 (fr)
WO (1) WO1996023964A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19629881A1 (de) * 1996-07-24 1998-01-29 Bayerische Motoren Werke Ag Ventiltrieb einer Brennkraftmaschine mit sich an einer Exzenterwelle abstützenden Schwinghebeln
DE10054798B4 (de) * 2000-11-04 2009-03-05 Schaeffler Kg Elektrisch angetriebene Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
DE10317508A1 (de) * 2003-04-16 2004-11-04 Daimlerchrysler Ag Vorrichtung zum Verstellen des Drehwinkels einer Nockenwelle gegenüber dem Drehwinkel einer Kurbelwelle einer Brennkraftmaschine
US20080017150A1 (en) * 2004-09-15 2008-01-24 Yamaha Hatsudoki Kabushiki Kaisha Variable Valve Drive Device, Engine, and Motorcycle
DE102005034777B3 (de) * 2005-07-26 2007-03-22 Daimlerchrysler Ag Nockenwelle
DE102005053119A1 (de) * 2005-11-08 2007-05-10 Robert Bosch Gmbh Vorrichtung zur Verstellung der relativen Drehwinkellage zwischen Nockenwelle und Antriebsrad
CN111852813A (zh) * 2020-07-02 2020-10-30 王彦彬 一种直线运动输出机构

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1311562A (en) * 1969-06-27 1973-03-28 Ass Eng Ltd Device for moving a cam relative to its driving shaft
US3633555A (en) * 1969-06-27 1972-01-11 Ass Eng Ltd Variable camshaft mechanism
GB2133465A (en) * 1982-12-24 1984-07-25 Ford Motor Co I.c. engine camshaft drive mechanism
GB2268570B (en) * 1989-10-13 1994-03-30 Rover Group An internal combustion engine camshaft drive mechanism
JP2644408B2 (ja) * 1991-03-29 1997-08-25 アーウィン コロステンスキー 内燃機関の連続可変バルブタイミング機構
JP3177532B2 (ja) * 1992-01-27 2001-06-18 株式会社ユニシアジェックス 内燃機関の吸排気弁駆動制御装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9623964A1 *

Also Published As

Publication number Publication date
AU4384896A (en) 1996-08-21
DE59604840D1 (de) 2000-05-04
EP0807206B1 (fr) 2000-03-29
DE19502834A1 (de) 1996-08-08
WO1996023964A1 (fr) 1996-08-08

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