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WO1996011325A1 - Dispositif de commande de soupapes d'admission/echappement destine a un moteur a quatre temps - Google Patents

Dispositif de commande de soupapes d'admission/echappement destine a un moteur a quatre temps Download PDF

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Publication number
WO1996011325A1
WO1996011325A1 PCT/JP1995/002063 JP9502063W WO9611325A1 WO 1996011325 A1 WO1996011325 A1 WO 1996011325A1 JP 9502063 W JP9502063 W JP 9502063W WO 9611325 A1 WO9611325 A1 WO 9611325A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
valve
cam follower
exhaust
engine
Prior art date
Application number
PCT/JP1995/002063
Other languages
English (en)
Japanese (ja)
Inventor
Hiroomi Ogasawara
Original Assignee
Ogasawara Precision Engineering Ltd.
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 Ogasawara Precision Engineering Ltd. filed Critical Ogasawara Precision Engineering Ltd.
Priority to DE19581378T priority Critical patent/DE19581378T1/de
Publication of WO1996011325A1 publication Critical patent/WO1996011325A1/fr

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
    • F01L13/0063—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
    • F01L1/12—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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/18—DOHC [Double overhead camshaft]

Definitions

  • the present invention relates to a device for changing the operation timing of a supply / exhaust valve of a four-cycle engine, and more particularly to a device for changing the timing of transmitting the operation of a cam to a valve and the valve lift.
  • the supply and exhaust of the engine is performed by operating at least one of the intake and exhaust valves according to the rotation of the cam.
  • the charging efficiency and the combustion efficiency are not the best if the timing of the supply and exhaust of the engine is not changed between the low and high engine speeds. In other words, the higher the engine speed, the faster the supply and exhaust timing needs to be.
  • VTEC and MIVEC two types of cams
  • a helical gear called VANOS is used to change the force acting on at least one of the cam-operated intake and exhaust valves, and the helicopter gear rotates according to the separately detected engine speed. In some cases, the degree of action fe3 ⁇ 4 is changed.
  • the present invention has been made in consideration of the above points, and has as its object to provide a four-stroke engine integrated exhaust valve control device that can perform variable supply and exhaust according to the engine speed in a simple manner.
  • a cam that determines the timing of at least one of an air supply valve and an exhaust valve of the engine, and a valve body that is pressed in accordance with the rotation of the cam and pushes down at least one of the air supply valve and the exhaust valve.
  • the cam operation of the cam is applied to the valve body between the cam and the valve body, and ⁇ is changed according to an external force.
  • a four-cycle engine wherein a cam follower that changes the timing and the valve lift amount of the cam that moves the cam to the valve body by changing the contact position with respect to the cam, or a rocker arm is further inserted.
  • Lined exhaust valve control device
  • the operating timing of at least one of the exhaust and exhaust valves of the engine determined by the cam is transmitted to the valve via the cam follower.
  • the cam follower can change its length when an external force is applied, and by changing the posture, the phase angle position that contacts the cam changes, so the timing of receiving the operation from the cam changes.
  • the timing of the valve element changes to change the timing relationship between the cam operation and the operation of the valve element, so that the engine charging efficiency and combustion efficiency corresponding to the engine speed can be optimized.
  • changing the posture of the cam follower changes the contact position force with the valve body, so the valve lift also changes.
  • the movement of the cam follower may be further transmitted to the valve via a rocker arm.
  • FIG. 1 (a) is a vertical cross-sectional view of the supply and discharge periphery of a four-stroke engine to which the present invention is applied
  • FIG. 1 (b) is a partial detailed view of FIG. 1 (a).
  • FIG. 2 is a diagram for explaining the operation of the supply / exhaust timing according to the present invention.
  • FIG. 2 (a) shows the case of normal timing
  • FIG. 2 (b) shows the case of early timing.
  • FIG. 2 (a) shows the case of normal timing
  • FIG. 2 (b) shows the case of early timing.
  • FIG. 3 is a view showing a rotary member 3 in the example of FIG.
  • FIG. 4 is a schematic diagram illustrating the operation of the cam follower in the example of FIG. 1.
  • FIG. 5 is a simplified diagram of FIG. 4 illustrating the operation of the cam follower in the example of FIG. 1;
  • FIG. 6 is a characteristic diagram showing the relationship between the inclination angle of the cam follower and the rate of change of the valve lift in the example of FIG.
  • FIG. 7 is a diagram showing the relationship between the inclination angle of the cam follower and the change Ut in the clearance of ⁇ which comes into contact with the cam follower in the example of FIG.
  • FIG. 8 is a view showing another example of the angle H of the present invention.
  • FIG. 8 (a) shows a state viewed from the same angle as FIG. 1, and
  • FIG. 8 (b) shows an X-X of FIG. It shows the condition viewed along the direction.
  • FIG. 9 is a longitudinal sectional view showing the supply and discharge of another HJI example of the present invention.
  • FIG. 10 is a diagram for explaining the change ⁇ b operation of the supply / exhaust timing according to the present invention.
  • FIG. 10 (a) shows the case of normal timing
  • FIG. 10 (b) shows the case of early timing.
  • FIG. 11 is a view showing another embodiment of the present invention.
  • FIG. 11 (a) shows a state viewed from the same angle as FIG. 9, and
  • FIG. 11 (b) shows a state of FIG. 11 (a).
  • X shows the state viewed along the X direction.
  • FIGS. 1 (a) and 1 (b) show, as an Hlfe form of the present invention, a vertical cross section around a supply / exhaust valve of a four-stroke engine. As shown, the engine or air-fuel mixture is introduced into the cylinder through an air supply port 10 and is discharged from an exhaust port 20 after compression and combustion.
  • FIG. 1 shows only the details of pfling the air supply valve provided in the air supply hole 10 and omits the other components.The same configuration is applied to the exhaust valve provided in the exhaust hole 20. Or ⁇ !
  • the fl of the air supply valve is controlled by the operation of the cam 1.
  • the cam 1 rotates clockwise in the figure synchronously with the rotation of the engine, pushes down the valve body via another member at a predetermined rotation position against the extension of the spring incorporated in the air supply valve, and forms a line. Air is supplied to the cylinder from the pore 10.
  • the cam follower 2 is formed in a columnar shape as shown in FIG. 1 (a), and is accommodated in a through-hole provided in a cylindrical rotating body 3 so as to be movable in the axial direction or "5J-capable.” As shown in Fig. 1 (b), the cam follower 2 may have a large diameter at the contact portion with the cam and a thinner guide portion, that is, may have a so-called mushroom-like shape.
  • the pressing force of the body is fitted to the valve body 8 via the hemispherical body 4.
  • the hemispherical body 4 is in sliding contact with the upper surface of the valve body 8 in the figure, and the pressing force from the cam follower 2 is applied to the valve. A downward force in the figure is given to the body 8. Therefore, a force for pushing down the valve body 8 against the extension force of the spring 7 is given to the upper end face in the drawing of # ⁇ * 8.
  • valve element 8 When the valve element 8 is pushed down, the end of the air supply hole closed by the valve element 8 is opened, and the air is communicated with the air supply hole 10 and the cylinder, and a solid air is performed.
  • a similar valve is provided between the exhaust port 20 and the cylinder. An operation for exhausting by the operation is performed.
  • FIG. 2A and 2B are diagrams for explaining the operation of changing the supply / exhaust timing according to the present invention.
  • FIG. 2A shows the case of normal timing
  • FIG. 2B shows the case of early timing.
  • the cam 1 rotates clockwise in the figure and comes into contact with the upper surface of the cam follower 2 in the figure.
  • the cam follower 2 is pushed down in the axial direction along the through hole of the rotating body 3 and pushes down the hemispherical body 4.
  • the rotating body 3 is rotated counterclockwise by an angle 0 as compared with the state of the same figure (a), and the cam follower 2 is in an inclined state with respect to the cam 1. .
  • the cam follower 2 first comes into contact with the cam 1 at the right end of the upper surface in the figure.
  • the upper surface of the cam follower 2 is shifted rightward in the drawing when viewed from the center axis of the cam follower 2, and thus is the portion of the upper surface of the cam follower 2 that comes into contact with the cam 1 first. Therefore, in the case of FIG. 7 (a), the cam follower 2 responds to 3 ⁇ ⁇ of the cam 1 earlier than in FIG. 7 (a). If the inclination angle of the cam follower 2 is reversed in the clockwise direction, the cam follower 2 responds to the movement of the cam 1 with a delay.
  • the cam follower 2 changes the force with respect to the cam 1 in accordance with the engine speed. If the cam follower 2 contacts the cam 1 at ⁇ shown in the same figure (a) when the engine speed is high, the cam follower 2 contacts the cam 1 at ⁇ shown in the same figure (b) at high speed. For example, by rotating the rotating body 3 through a control mechanism (not shown) or a link mechanism operated by an actuator such as a hydraulic pressure, supply and exhaust at high speed is performed earlier than engine rotation. .
  • FIG. 3 shows the shape of the rotating body 3.
  • the rotating body 3 is The rotating body 3 has two through holes 3 a, 3 a which are substantially cylindrical in shape, are arranged side by side along the longitudinal direction thereof, and extend from one of the peripheral surfaces of the rotating body 3 to the other.
  • the cam follower 2 is accommodated in the through hole 3a so as to be movable in the axial direction in the through holes 3a and 3b.
  • a longer rotating body 3 common to a plurality of cylinders and having only two valves in the DOHC engine may be formed.
  • At least one end surface of the rotating body 3 is provided with a connecting portion 3b, and the connecting portion 3b is subjected to IE® connection with a control mechanism or a hydraulic device provided by a link mechanism (not shown).
  • IE® connection with a control mechanism or a hydraulic device provided by a link mechanism (not shown).
  • FIGS. 6 and 7 are schematic diagrams for explaining how the clearance between the cam follower pushed up by the valve spring and the rotation limit position for taking two forces changes.
  • the cam follower 2 has a total length St of 5 O mm, and pivots to a position at an angle 0 with a point at a distance S from the contact surface with the cam 1 as a fulcrum.
  • the lower end of the cam follower 2 is in contact with the valve body 8 via the hemispherical body 4.
  • This schematic diagram shows a state in which the cam follower 2 abutting on the cam 1 is in an upright state, which is a reference state, and a state in which the cam follower 2 rotates about the rotation center C f and rotates to a position of an angle 0 indicated by the idea. .
  • FIG. 6 is a characteristic diagram obtained by performing a simulation under the conditions of FIG.
  • the horizontal axis indicates the tilt angle 0 of the cam follower 2
  • the vertical axis indicates the lift of a valve (not shown).
  • the valve lift is +8 when the tilt angle is 0.
  • the valve lift within the above range Rate is obtained.
  • the change of the valve lift can be estimated by the following formula (1).
  • FIG. 7 is a characteristic diagram obtained by performing a simulation under the conditions of FIG. 4 in the same manner as in FIG. 6, in which the inclination angle 0 of the cam follower 2 is plotted on the horizontal axis, and the change in the clearance of the cam follower 2 ( ⁇ 1 is plotted on the vertical axis).
  • the clearance between the cam and the cam follower must be within a range that can absorb this change, and the clearance change amount 1 can be obtained by the following equation (2).
  • the change in clearance bS can be kept within 1 to around 8 °.
  • the valve opening angle can be reduced by arranging the clearance in a direction to increase the clearance.
  • FIGS. 8A and 8B show another example of the present invention, in which the cam follower 12 is formed in an umbrella shape and supported by a ring 13.
  • the ring 13 is supported by the cylinder head by a force (not shown) ⁇ a well-known structure.
  • the ring 13 may be not cylindrical but notched as long as it can support the cam follower 12.
  • the upper surface in the figure of ##: 14 is an arc surface with a radius R centered on the cam shaft.
  • FIG. 9 shows a state similar to that of FIG. 1 according to still another embodiment of the present invention.
  • C FIG. 9 also shows only the opening of the air valve provided in the air supply hole 10 in detail. The other components are omitted. The same configuration can be applied to the exhaust provided in the exhaust hole 20.
  • the p3 ⁇ 4l of the air supply valve is controlled by the operation of the cam 1.
  • the cam 1 rotates clockwise in the figure synchronously with the rotation of the engine, stakes at a predetermined rotation position under the tension of the spring incorporated in the lined air valve, pushes down the valve body via another member, and supplies the power. Vent from cylinder 10 to cylinder.
  • the main elements for transmitting the cam operation of the cam 1 to the air valve at this time are the cam follower 2 and the rocker arm 5 as a valve F ⁇ member.
  • the cam follower 2 is formed in a columnar shape, and is accommodated in a through hole provided in the cylindrical rotating body 3 so as to have an axial moving force. Further, as shown in FIG. 9 (b), the cam follower 2 may have a so-called mushroom-like shape in which the diameter of the contact portion with the force is large and the guide portion is thinner than that.
  • the pushing force of the valve body by the cam follower 2 is transmitted to the rocker arm 5 through the hemispherical body 4.
  • the hemisphere 4 slides on the upper surface of the rocker arm 5 in the figure.
  • the cam follower 2 is being touched, and the pressing force from the cam follower 2 is applied to the mouth kicker arm 5 downward in the figure.
  • the rocker arm 5 rotates counterclockwise in the figure, and applies a force to push down the valve body 8 against the extension force of the spring 7 to the illustrated upper end of the valve body 8 via the spherical body 6.
  • the rocker arm 5 receives a clockwise acting force due to the extension force of the spring 7, and rotates to a preset operation position around a rotation center near the right end in the figure. Then, it receives an acting force from the cam follower 2 and gives an acting force to # ⁇ * 8.
  • the rocker arm 5 is a member for applying the acting force received from the force follower 2 to the valve element 8. If the point where the acting force is received from the force follower 2 and the point applied to the valve element 8 are only slightly small in position and are not separated from each other, the strength of the rocker arm 5 does not need to be increased so much.
  • valve element 8 When the valve element 8 is pushed down, the end of the air supply hole closed by the valve element 8 opens, and the air hole 10 and the cylinder are connected to supply air.
  • the same operation for exhaust is performed between the exhaust hole 20 and the cylinder by the same valve operation.
  • FIG. 10 is a diagram for explaining the operation of changing the supply / exhaust timing in the embodiment of FIG. 9.
  • FIG. 10 (a) shows the case of normal timing
  • FIG. 10 (b) shows the case of early timing. Each is shown.
  • the cam 1 rotates clockwise in the figure and comes into contact with the upper surface of the cam follower 2 in the figure.
  • the cam follower 2 is pushed down in the axial direction along the through hole of the rotating body 3, and pushes down the hemispherical body 4 to apply a force to the cam follower 5.
  • the cam follower 2 changes ⁇ with respect to the cam 1 in accordance with the engine speed. If the cam follower 2 contacts the cam 1 at ⁇ shown in the same figure (a) when the engine speed is low, the cam follower 2 contacts the cam 1 at ⁇ shown in the same figure (b) at high speed. For example, by rotating the rotating body 3 through a link (not shown) that is controlled by a control motor or an actuator such as a hydraulic pressure, air supply and exhaust at a high speed are performed earlier than the engine rotation. .
  • FIGS. 11A and 11B show another example of the present invention, in which a cam follower 12 is formed in an umbrella shape and supported by a ring 13.
  • the ring 13 is supported by a cylinder head by a well-known configuration (not shown).
  • the ring 13 may be not cylindrical but notched as long as it can support the cam follower 12.
  • the position of the cam follower 2 may be offset in the advance direction, that is, in the direction shown in the figure with respect to the center position of the cam 1.
  • the cam follower since the operation of the cam is transmitted to the valve body via a force follower that changes the contact position with respect to the cam when the external force is applied and the force changes, the cam follower can be changed according to the engine speed.
  • the operation to the valve body can be performed at timing that changes according to the speed.
  • the operation of at least one of the supply valve and the exhaust valve can be changed according to the engine 3 ⁇ 4S.
  • the contact position between the cam follower and the valve body the force to change the valve lift can be achieved.
  • the present invention since the present invention has the structure of the upper part of the cylinder head of the engine, the present invention can be similarly applied to a case where the present invention is applied to an existing engine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

Domaine industriel d'application: on décrit un dispositif destiné à modifier le calage de la distribution des soupapes d'admission et d'échappement dans un moteur à quatre temps, et plus particulièrement un dispositif destiné à modifier une distribution en fonction de laquelle le mouvement de la came est transmis à une soupape et à un poussoir de soupape. Problème: un objet de l'invention est de fournir un dispositif d'admission/échappement variable qui soit simple à construire et capable de commander l'admission et l'échappement en fonction de la vitesse du moteur. Moyens de résoudre le problème: on décrit un dispositif de commande d'une soupape d'admission et d'échappement qui est destiné à un moteur à quatre temps et comprend une came (1) servant au calage de la distribution d'au moins une des soupapes d'admission et d'échappement, ainsi qu'un disque (8, 14) de soupape conçu pour fonctionner en étant comprimé vers le bas en conformité avec la rotation de la came, afin de comprimer vers le bas au moins un des disques des soupapes d'admission et d'échappement, ce dispositif étant caractérisé en ce qu'une contre-came (2) ou la contre-came et un culbuteur (5, 15) sont insérés entre la came et le disque de soupape, la contre-came étant conçue non seulement pour transmettre le fonctionnement de la came au disque de la soupape, mais également pour être capable de modifier son comportement en fonction d'une force externe, de manière à changer la position de contact par rapport à la came, modifiant ainsi la distribution du mouvement de la came transmis au disque de la soupape et au poussoir de celle-ci.
PCT/JP1995/002063 1994-10-11 1995-10-09 Dispositif de commande de soupapes d'admission/echappement destine a un moteur a quatre temps WO1996011325A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19581378T DE19581378T1 (de) 1994-10-11 1995-10-09 Einlaß-/Auslaßventil-Steuermechanismus für einen Viertaktmotor

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP24534294A JPH08109812A (ja) 1994-10-11 1994-10-11 ４サイクルエンジンの給排気弁制御装置
JP6/245342 1994-10-11

Publications (1)

Publication Number Publication Date
WO1996011325A1 true WO1996011325A1 (fr) 1996-04-18

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PCT/JP1995/002063 WO1996011325A1 (fr) 1994-10-11 1995-10-09 Dispositif de commande de soupapes d'admission/echappement destine a un moteur a quatre temps

Country Status (3)

Country Link
JP (1) JPH08109812A (fr)
DE (1) DE19581378T1 (fr)
WO (1) WO1996011325A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7380531B2 (en) 2005-04-01 2008-06-03 Schaeffler Kg Variable valve drive for changing the control timing of cam-actuated gas-exchange valves

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10036373A1 (de) * 2000-07-18 2002-02-14 Herbert Naumann Hubventilsteuerungen
JP4896817B2 (ja) * 2006-07-25 2012-03-14 本田技研工業株式会社 内燃機関の可変動弁装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6182009U (fr) * 1984-11-05 1986-05-30
JPS6272410U (fr) * 1985-10-28 1987-05-09
US5056476A (en) * 1990-08-28 1991-10-15 King Brian T Variable valve duration and lift for an internal combustion engine
JPH05508205A (ja) * 1990-02-16 1993-11-18 グループ　ロータス　リミテッド 弁制御手段
JPH06185324A (ja) * 1992-12-15 1994-07-05 Toyota Motor Corp 内燃機関のバルブタイミングおよびリフト制御装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6182009U (fr) * 1984-11-05 1986-05-30
JPS6272410U (fr) * 1985-10-28 1987-05-09
JPH05508205A (ja) * 1990-02-16 1993-11-18 グループ　ロータス　リミテッド 弁制御手段
US5056476A (en) * 1990-08-28 1991-10-15 King Brian T Variable valve duration and lift for an internal combustion engine
JPH06185324A (ja) * 1992-12-15 1994-07-05 Toyota Motor Corp 内燃機関のバルブタイミングおよびリフト制御装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7380531B2 (en) 2005-04-01 2008-06-03 Schaeffler Kg Variable valve drive for changing the control timing of cam-actuated gas-exchange valves

Also Published As

Publication number Publication date
DE19581378T1 (de) 1996-12-19
JPH08109812A (ja) 1996-04-30

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