EP0717174A1 - Système de commande de soupape pour moteur à combustion interne - Google Patents

Système de commande de soupape pour moteur à combustion interne Download PDF

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Publication number
EP0717174A1
EP0717174A1 EP95119507A EP95119507A EP0717174A1 EP 0717174 A1 EP0717174 A1 EP 0717174A1 EP 95119507 A EP95119507 A EP 95119507A EP 95119507 A EP95119507 A EP 95119507A EP 0717174 A1 EP0717174 A1 EP 0717174A1
Authority
EP
European Patent Office
Prior art keywords
shaft
rocker arm
cam
valve
lift timing
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Withdrawn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
EP95119507A
Other languages
German (de)
English (en)
Inventor
Shigeaki c/o Isuzu Motors Ld. Horinchi
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.)
Isuzu Motors Ltd
Original Assignee
Isuzu Motors 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
Priority claimed from JP33259194A external-priority patent/JPH08165910A/ja
Priority claimed from JP2112995A external-priority patent/JPH08189318A/ja
Priority claimed from JP7046241A external-priority patent/JPH08218831A/ja
Application filed by Isuzu Motors Ltd filed Critical Isuzu Motors Ltd
Publication of EP0717174A1 publication Critical patent/EP0717174A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—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
    • F01L1/205—Adjusting or compensating clearance by means of shims or the like
    • 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
    • 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
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors
    • 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
    • F01L2820/03—Auxiliary actuators
    • F01L2820/034—Pneumatic engines

Definitions

  • This invention relates to a valve operating system for an internal combustion engine having a rocker arm permitting alteration of valve lift timing by shifting its rocking fulcrum.
  • Some valve operating systems have a rocker arm, whose rocking fulcrum can be shifted, provided at a position between a cam for supplying a driving force for moving a valve to open or close and the stem of the valve to which the driving force is to be delivered.
  • Valve lift timing can be altered as the case demands by shifting the rocking fulcrum of the rocker arm along the circle with the center of the cam as its center.
  • rocker arm not permitting alteration of rocking fulcrum is referred to as a first rocker arm
  • rocker arm permitting alteration of rocking fulcrum is referred to as a second rocker arm.
  • Fig. 1 shows such conventional valve operating system for an internal combustion engine.
  • numeral 9 designates a cam, 8 a shaft, 8C a center of shaft 8, 12 a second rocker arm, 15 a shaft, 15C a center of shaft 15, 64 a first rocker arm, 6-1 a guide groove, 7 a shaft, 1 a valve, 20 a lever for altering valve lift timing, and A and B arrows.
  • Both of the first rocker arm 6 and the second rocker arm 12 are of end pivot type having a rocking fulcrum at one end.
  • the shaft 8 of the cam 9 and the shaft 15 of the second rocker arm 12 are supported by the lever 20 for altering valve lift timing.
  • the cam 9 is in sliding contact with the upper surface of the second rocker arm 12, and the tip end of the second rocker arm 12 is fitted with the guide groove 6-1 provided in the upper portion of the rocker arm 6 to contact.
  • the guide groove 6-1 is provided for the tip end not to come out of the rocker arm 6.
  • the lower end of the rocker arm 6 is in contact with the stem of the valve 1, with the valve 1 being opened upon the stem being pushed downward.
  • Fig. 2 illustrates the lever 20 for altering valve lift timing. Signs correspond to those in Fig. 1, with 20-1 and 20-2 designating supporting holes, 20-3 an end-connecting portion, 21 a return spring, and 22 a wire. Both ends of the shaft 8 of the cam 9 penetrate through the holes 20-1, whereas both ends of the shaft 15 of the second rocker arm 12 penetrate through the supporting holes 20-2. One end of the wire 22 is connected to an about central portion of the end-connecting portion 20-3, and the return spring 21 is provided on each side of the lever 20 for altering valve lift timing.
  • the lever 20 for altering valve lift timing is swung in the direction shown by the arrow B when the wire 22 is pulled in the direction shown by the arrow, or is swung in the direction shown by the arrow A due to the biasing force of the return spring 21 when the wire 22-pulling force is weakened.
  • This swinging motion causes the shaft 15 penetrating through the supporting hols 20-2 to swing in the direction shown by the arrow A or B as shown in Fig. 1.
  • the direction shown by the arrow A or B is along the circle with the center 8C of the shaft 8 of the cam 9 as its center.
  • Fig. 3 is a graph showing a valve lift curve, with time (of timing) as abscissa and valve-lifting degree as ordinate.
  • the valve lift curve is a characteristic curve showing the relation between the valve-lifting degree and lift timing.
  • Curve S is a curve when the center 15C of the shaft 15 is at a standard position.
  • Curve A is a curve when the center 15C is shifted in the circular direction A shown in Fig. 1 with the center 8C of the shaft 8 as a center of the circle. Such shift is suited for obtaining a higher power from an internal combustion engine.
  • Curve B is a curve when shifted in the direction B. Such shift is suited for obtaining a lower power from the internal combustion engine.
  • valve operating systems for an internal combustion engine as described above are described in, for example, Japanese Unexamined Patent Publication No. 64-53009.
  • a first problem is that, when employed in a multi-cylinder internal combustion engines, quite a large power is required for driving the valve operating system.
  • FIG. 1 there exist several slidingly contacting portions in the aforesaid valve operating system on the driving force-delivering way between the cam 9 and the valve 1. That is, the cam 9 and the second rocker arm 12 are in sliding contact with each other, and the tip end of the second rocker arm 12 and the guide groove 6-1 are in sliding contact with each other. In delivering a driving force through such sliding contact, not only a driving force but a force overcoming the friction force of the sliding contact on the driving force-delivering way must be provided.
  • multi-cylinder engines require quite a strong force since the aforesaid friction force is multipled, though not so much with single cylinder engines. Since the force for rotating the cam 9 is also provided from the engine, there eventually results an increased engine load.
  • a second problem of the aforesaid conventional valve operating system for an internal combustion engine is that the cam 9 and the second rocker arm 12 can get out of relative position or deviate in the axial direction, which leads to a decrease in contact area therebetween, resulting in such troubles as an increase in surface-to-surface pressure per unit area applied to the contact surfaces.
  • Fig. 4 illustrates the cam 9 and the second rocker arm 12 in the axially deviating state.
  • D represents the deviation degree.
  • the second rocker arm 12 is supported in relation to the shaft 8 of the cam 9 by means of the lever 20 for altering valve lift timing as is shown by Fig. 1.
  • no special means are provided for properly positioning them in the longitudinal or axial direction of the shaft.
  • the cam 9 and the second rocker arm 12 in contact with each other can deviate relatively in the axial direction.
  • the contact area between the cam 9 and the second rocker arm 12 decreases. Since the force delivered from the cam 9 is the same, the force applied to unit area of the contact area (surface-to-surface pressure per unit area) increases, which causes damage of the contact surface.
  • a third problem with the aforesaid conventional valve operating system for an internal combustion engine is that, since a controlling member for altering valve lift timing has not enough rigidity (to deliver controlling force), control of valve lift timing has not been conducted with high accuracy and responsiveness particularly in a multi-cylinder internal combustion engine.
  • valve lift timing-altering lever 20 is pulled by pulling the valve lift timing-altering lever 20 with the wire 22 or by allowing to return to place through the biasing force of the return spring 21, as shown in Fig. 1.
  • wires will be stretched to some extent, and strength of the return spring will change after long use.
  • all valves are different from each other in valve-operating conditions, and forces resisting the controlling force by the wire 22 or the return spring 21 vary.
  • a force delivered to each second rocker arm (12 in Fig. 1) from the spring (2 in Fig. 5) provided around the valve differs depending upon the position of each valve (1 in Fig. 1) in each cylinder. Therefore, in the case of returning in the direction shown by the arrow A through the biasing force of the return sprig 21, resisting force differs depending upon the stage. Therefore, when the resisting force is large, the controlling force can not be delivered rapidly, failing to conduct the control with high accuracy and responsiveness.
  • the present invention provides a valve operating system for an internal combustion engine having a rocker arm permitting alteration of valve lift timing by shifting the rocking fulcrum, in which a roller for attaining a rolling contact is provided at least at one of the contacting positions on the driving force-delivering way between a cam for providing a driving force and a valve, and one contact surface on the driving force-delivering way is made a circular surface with the center of said cam as its center.
  • a first and a second rocker arms may be used as the rocker arm.
  • the first rocker arm has at one end a means for fittingly contacting with the aforesaid stem of the valve and at the other end a circular surface with the center of the aforesaid cam as its center
  • the second rocker arm has a rocking fulcrum shiftable upon alteration of valve lift timing and has at the rocking tip end a first roller in contact with said circular surface and a second roller in contact with said cam with both rollers on the same shaft.
  • the present invention provides a valve operating system for an internal combustion engine having a rocker arm permitting alteration of valve lift timing by shifting the rocking fulcrum, in which a bracket, engagedly fitted to a cam shaft, through which a shaft for said rocker arm penetrates at its one end and which is engagedly fitted to a shaft of the cam functioning as a source of driving force is provided, said engaged fitting being formed by a combination of a depression and a projection to prevent deviation in the axial direction of the shaft.
  • the present invention provides a valve operating system for an internal combustion engine having a rocker arm permitting alteration of valve lift timing by shifting the rocking fulcrum, in which a bracket, engagedly fitted to a cam shaft, which intervenes between said shaft and a cam shaft; a valve lift timing-altering shaft rockable by the force delivered from a driving means; and a fork lever one end of which is fixed to said valve lift timing-altering shaft and whose fork grooves are fitted to said shaft are provided
  • the valve operating system may have a bracket, engagedly fitted to a cam shaft, which intervenes between said shaft and a cam shaft; a valve lift timing-altering shaft rockable by the force delivered from a driving means; and a gear mechanism having a gear fixed to said valve lift timing-altering shaft and a gear engaged with the gear and fixed to said shaft.
  • Fig. 1 illustrates a conventional valve operating system of an internal combustion engine.
  • Fig. 2 illustrates a lever for altering valve lift timing.
  • Fig. 3 is a graph showing a valve lift curve.
  • Fig. 4 illustrates axial deviation between a cam and a second rocker arm.
  • Fig. 5 illustrates a first example of the present invention.
  • Fig. 6 illustrates a second example of the present invention.
  • Fig. 7 illustrates a third example of the present invention.
  • Fig. 8 illustrates a fourth example of the present invention.
  • Fig. 9 illustrates a fifth example of the present invention.
  • Fig. 10 illustrates a sixth example of the present invention.
  • Fig. 11 illustrates a seventh example of the present invention.
  • Fig. 12 illustrates an eighth example of the present invention.
  • Fig. 13 is a plan view of a second rocker arm.
  • Fig. 14 is a perspective view of the eighth example of the present invention.
  • Fig. 15 illustrates a deviation-preventing mechanism of the present invention in a valve operating system.
  • Fig. 16 illustrates a bracket to be engagedly fitted to a cam shaft.
  • Fig. 17 is a perspective view of a ninth example of the present invention.
  • Fig. 18 illustrates a bracket of the ninth example to be engagedly fitted to a cam shaft.
  • At least one of the slidingly contacting portions existing mainly on the driving force-delivering way between cam and valve is replaced by a rolling contact portion, in a valve operating system of an internal combustion engine having a rocker arm permitting alteration of valve-lifting time by shifting rocking fulcrum, thus reducing the necessary force for operating the valve operating system.
  • axial deviation between the cam 9 which delivers a force to operate the valve and the second rocker arm 12 is prevented in addition to the reduction of the force for operating the valve operating system by using rollers.
  • Fig. 5 shows a first example of the present invention. Signs correpond to those described in Fig. 1.
  • Numeral 2 designates a spring, 3 a spring sheet, 4 a cotter, 5 an adjuster, 10 a roller, 11 a shaft, 12-1 a contact surface, 13 a roller, and 14 a shaft.
  • the same signs as in Fig. 1 have the same meaning, description thereof being omitted.
  • the roller 13 is fitted to the tip end of the second rocker arm and is in contact with the cam 9.
  • the shaft 14 is a shaft for the roller 13.
  • One end of the first rocker arm 6 is fittingly contacted with the valve stem of the valve 1 through the adjuster 5, and the other end has a roller 10 fitted thereto by the shaft 11.
  • the contact surface 12-1 of the second rocker arm 12 is in contact with the first rocker arm 6 through the roller 10.
  • the contact surface 12-1 is formed as a circular surface with the center 8C of the shaft as its center. Because, such circular form serves for the first rocker arm 6 not to be shifted upon shifting the center 15C of the shaft 15 in the direction of A or B. (In the following other examples, circular surfaces with the center 8C as their center, if used, are made circular for the same reason.) Since the center 15C is shifted in the direction shown by the circular arrow A or B with the center 8C as its center, the contact surface 12-1 which is in a circular form also with the center 8C as its center merely migrates along the same circle when the center 15C is shifted, thus not pushing the rocker arm 6 upword or downward.
  • Fig. 6 illustrates a second example of the present invention. Signs correspond to those in Fig. 5, with 6-1 designating a contact surface, 16 a roller and 17 a shaft.
  • rollers are provided only in the second rocker arm.
  • the roller 13 is fitted in the middle of the second rocker arm 12, and the roller 16 at the tip end.
  • the cam 9 is in contact with the roller 13, and the first rocker arm 6 is in contact with the roller 16.
  • Fig. 7 illustrates a third example of the present invention.
  • Fig. 7 (a) and (b) respectively illustrate two embodiments of the third example. Signs correspond to those in Figs. 5 and 6.
  • the third example is intended to decrease production cost, reduce cam-driving force and lower height of the valve operating system by using only one roller.
  • the cam 9 and the second rocker arm 12 are in contact with each other through the roller 13, but the contact surface of the second rocker arm 12 and the contact surface 6-1 of the first rocker arm 6 are in contact with each other without any roller. Since only one roller is used for the contact portion with the cam 9, friction force is larger than in the example wherein rollers are used in all contact portions (for example, Fig. 6). However, omission of one roller serves to lower the height of the valve operating system and decrease production cost in comparison with such examples as shown by Fig. 6. Therefore, in the case where the number of cylinders is not so large, this example suffices.
  • Fig. 8 illustrates a fourth example of the present invention. Signs correspond to those in Fig. 7. This example is also intended to decrease production cost, reduce the force for driving a cam, and lower the height of valve operating system by employing only one roller.
  • a surface 12-2 in contact with the cam 9 of the second rocker arm 12 is made flat, and a surface 12-1 in contact with the roller 10 of the first rocker arm 6 is of a circular shape with the center 8C of the shaft 8 as its center.
  • the fourth example is different from the third example in the position to which the roller is fitted.
  • the roller is fitted to the second rocker arm 12, whereas in the fourth example, the roller is fitted to the first rocker arm 6.
  • Fig. 9 illustrates a fifth example of the present invention.
  • the first rocker arm 6 is of a so-called end pivot type wherein the shaft 7 is provided at one end section.
  • Two rollers 10 and 13 are disposed in an in-line manner as in the example shown by Fig. 5.
  • the contact surface 12-1 of the second rocker arm 12 is of a circular shape with the center 8C of the cam 9 as its center.
  • Fig. 10 illustrates a sixth example of the present invention. Signs correspond to those in Figs. 5 and 6, with numeral 18 designating a tappet and 19 a shim. (Additionally, since only the first rocker arm 6 is used as the rocker arm in this example, it is merely referred to as "rocker arm”.) This is an example of applying the present invention to a valve operating system of direct attack type.
  • the shim 19 is provided on top of the tappet 18 and in contact with the contact surface 6-1 of the end pivot type rocker arm 6.
  • the contact surface 6-1 is of a circular shape with the center 8C of the shaft 8 as its center.
  • the roller 10 is fitted to the rocker arm 6, and is in contact with the cam 9.
  • the contact between the rocker arm 6 and the cam 9 is a rolling contact with the roller therebetween, thus the force for driving the cam 9 being reduced.
  • valve-lifting degree and valve lift timing can be altered by shifting the center 7C of the sahft 7 of the rocker arm 6 in the direction A or B along the circle with the 8C of the shaft 8 of the cam 9 as its center. Since the contact surface 6-1 is of a circular shape with the center 8C of the shaft 8 as its center, it does not push the shim downward even when the center 7C of the shaft 7 is shifted as described above.
  • Fig. 11 illustrates a seventh example of the present invention. Signs correspond to those in Fig. 10, with 19-1 designating the surface of shim.
  • the shim surface 19-1 is of a circular shape with the center 8C of the shaft 8 of the cam 9.
  • the roller 10 fitted to the tip end of the rocker arm 6 is in contact with the shim surface 19-1.
  • the contact surface 6-1 of the rocker arm 6 is flat and is in sliding contact with the cam 9.
  • Fig. 12 illustrates an eighth example of the present invention.
  • Fig. 13 is a plan view of the second rocker arm 12 used in this example. Signs correspond to those in Figs. 5 and 6, with 13-1 and 13-2 designating rollers.
  • two rollers 13-1 and 13-2 are fitted at the tip end of the second rocker arm 12 on the same shaft (shaft 14). And, as is seen in Fig. 3, the roller 13-1 is in contact with the cam 9, whereas the roller 13-2 is in contact with the first rocker arm 6.
  • the two rollers are disposed within the plane in the longitudinal direction of the second rocker arm 12 or, so to speak, disposed in a spacially in-line manner. Therefore, height of the valve operating system becomes higher.
  • the eighth example is intended to lower the height of the system even slightly.
  • the two rollers 13-1 and 13-2 are disposed side by side in the transverse direction with respect to the longitudinal direction of the second rocker arm 12, and hence height of the valve operating system can be reduced in comparison with the examples shown in Figs. 5 and 6. As to other points, the same applies as the example shown in Fig. 6.
  • Fig.14 is a perspective view showing the main portion of the valve operating system of the eighth example of the present invention. Signs correspond to those in Fig. 12, with numeral 23 designating a bracket engagedly fitted to the cam shaft, 24 a shaft for altering valve lift timing, 25 a supporting member, 26 a fork lever, and 27 a pin.
  • the shaft 24 for altering valve lift timing is engagedly fitted to the supporting member 25, and a gear 32 is fitted at its end section and is engaged with a pinion 31.
  • the pinion 31 is connected to a motor 30.
  • the motor 30 Upon alteration of valve lift timing, the motor 30 is droven according to an order from a controller not shown to rotate the pinion 31 clockwise or counterclockwise, thus the valve lift timing-altering shaft 24 being rotated.
  • the fork lever 26 is fixedly fitted, at its one end, to the shaft 24 for altering valve lift timing with the aid of pins 27.
  • the shaft 15, which is a rocking axis of the second rocker arm 12, is fitted to the fork groove of the fork lever 26.
  • Fig 16 illustrates the bracket 23 to be engagedly fitted to the cam shaft.
  • Numeral 23-1 and 23-2 each designates a half-devided piece of the bracket, 23-3 a hole for penetration of shaft, 23-4 a bolt, and 23-5 a bolt hole.
  • the engaged fitting can be conducted by holding the shaft 8 between the half-devided pieces 23-1 and 23-2, then driving the bolts 23-4 into the bolt holes 23-5.
  • the shaft 15 shown in Fig. 14 penetrates through the shaft-penetrating hole 23 -3.
  • the shaft 15 of the second rocker arm 12 is fixedly supported to the non-shiftable shaft 24 for altering valve lift timing through the fork lever 26, and fixedly supported to the non-shiftable shaft 8 through the bracket 23 engagedly fitted to the cam shaft.
  • the shaft 15 can be shifted by the swinging motion of the fork lever 26, thereby valve lift timing being altered.
  • Controlling force for altering valve lift timing is delivered in the followng order: motor 30 (driving means) ⁇ pinion 31 ⁇ gear 32 ⁇ shaft 24 for altering valve lift timing ⁇ fork lever 26 ⁇ shaft 15 (final member to be driven).
  • the motor 30 used in this example as a means for driving the shaft 24 for altering valve lift timing may be replaced by an air cylinder as used in the next ninth example.
  • Fig. 15 illustrates a mechanism for preventing axial deviation in the valve operating system of the present invention. Signs correspond to those in Figs. 14 and 16, with numeral 8-1 designating a slidable bearing portion, 8-2 a bearing metal, 23-5 bolt holes and 23-6 a projection. The roller 13-1 in contact with cam 9 is fitted to the second rocker arm 12 (not shown in Fig. 15 for avoiding complication) which is axially supported by the shaft 15.
  • the shaft 8 has the slidable bearing portion 8-1 having a slightly larger diameter at a position at which the bracket 23 is engagedly fitted to the shaft 8.
  • On the surface of the slidable bearing portion 8-1 may be provided, if necessary, the bearing metal 8-2 for protecting abrasion.
  • the bearing metal 8-2 is provided when the bracket 23 is made of steel, but not provided when the bracket 14 is made of aluminum.
  • the bracket 23 has, at the position where it is to be engagedly fitted to the slidable bearing portion 8-1, projections 23-6 with a depression therebetween, the depression being used for the engagement.
  • the engaged fitting of the shaft 8 and the bracket 23 serves to prevent deviation (in the axial direction of the shaft 8). Since no deviation takes place, there occurs no increase in surface-to-surface pressure at the contact surfaces per unit area and, therefore, no damages of the contact surfaces.
  • Fig. 17 is a perspective view of a main portion of a ninth example of the present invention
  • Fig. 18 illustrates a bracket to be engagedly fitted to a cam shaft used in the ninth example.
  • Signs correspond to those in Example 14, with numeral 33 designating an air cylinder, 34 an air pipe, 35 a link, 36 a lever, 37 a gear, 38 and 39 pins, 40 a gear, 41 a bracket engagedly fitted to the cam shaft, 41-1 shaft-penetrating hole, 41-2 a depression for fitting, and L an arrow..
  • a first difference in comparison from the example shown in Fig. 14 lies in that a gear mechanism (37, 40) is used for delivering the motion of the shaft 24 for altering valve lift timing to the shaft 15.
  • a gear mechanism 37, 40
  • the gear 37 is fixedly fitted to the shaft 24 for altering valve lift timing with the aid of pins 38
  • the gears 40 are fixedly fitted to both ends of the shaft 15 with the aid of the pins 39.
  • the gears 37 and the gears 40 are engagedly disposed with each other.
  • a second difference lies in that an air cylinder 33 is used as a driving means for rotating the shaft 24 for altering valve lift timing.
  • the motor 30 is used.
  • a lever 36 is connected to one end of the shaft 24 for altering valve lift timing, and a piston axis is connected to the lever 36 through a link 35.
  • a controlling force is delivered through the link lever mechanism, thus the valve lift timing-altering shaft 24 being rotated in the corresponding direction.
  • An air supplied to the air cylinder 33 through an air pipe 34 is controlled by a controller not shown.
  • a third difference lies in that the bracket 41 is of a merely hanging type as shown in Fig. 18.
  • the shaft 13 penetrates through the shaft-penetrating hole 41-1, and a fitting depression 41-2 is hung upon the shaft 8.
  • controlling force for altering valve lift timing is delivered in the followng order: air cylinder 33 (driving means) ⁇ link 35 ⁇ lever 36 ⁇ shaft 24 for altering valve lift timing ⁇ gear 37 ⁇ gear 40 ⁇ shaft 13 (final member to be driven).
  • This force-delivering route is also constituted by mechanically strong constituents and, in this case, too, a highly rigid controlling system is realized.
  • air cylinder 33 used in this example as a means for driving the shaft 24 for altering valve lift timing may be replaced by a motor as used in the eighth example.
  • a mechanically strong mechanism such as a gear mechanism or a link lever mechanism is employed as a controlling force-delivering mechanism.
  • a highly rigid controlling system is realized.
  • controlling force can be delivered rapidly, thereby valve lift timing being able to be altered with high accuracy and responsiveness.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP95119507A 1994-12-12 1995-12-11 Système de commande de soupape pour moteur à combustion interne Withdrawn EP0717174A1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP33259194A JPH08165910A (ja) 1994-12-12 1994-12-12 内燃機関の動弁装置
JP332591/94 1994-12-12
JP2112995A JPH08189318A (ja) 1995-01-12 1995-01-12 内燃機関の動弁装置
JP21129/95 1995-01-12
JP46241/95 1995-02-10
JP7046241A JPH08218831A (ja) 1995-02-10 1995-02-10 内燃機関の動弁装置

Publications (1)

Publication Number Publication Date
EP0717174A1 true EP0717174A1 (fr) 1996-06-19

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Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0761935A2 (fr) * 1995-09-01 1997-03-12 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Entraînement de soupape variable, en particulier pour moteurs à combustion interne
EP0962629A2 (fr) 1998-06-05 1999-12-08 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Commande de soupape variable pour moteur à combustion interne
WO2000008309A1 (fr) * 1998-08-05 2000-02-17 Delphi Technologies, Inc. Mecanisme variable de commande de soupapes
FR2799792A1 (fr) * 1999-10-15 2001-04-20 Jean Louis Rico Moteur thermique a distribution variable
GB2357131A (en) * 1999-12-09 2001-06-13 Mechadyne Internat Plc Valve actuating mechanism
DE10036373A1 (de) * 2000-07-18 2002-02-14 Herbert Naumann Hubventilsteuerungen
EP1143119A3 (fr) * 2000-03-21 2003-01-29 Toyota Jidosha Kabushiki Kaisha Dispositif pour varier la phase et la course d'une soupape et appareil de contrôle de volume d'air d'admission
WO2003008772A1 (fr) * 2001-07-17 2003-01-30 Thyssenkrupp Automotive Ag Commande variable de course de soupape
US6584943B1 (en) * 2002-09-18 2003-07-01 Daimlerchrysler Corporation Variable compound rocker system for push rod and overhead camshaft engines
WO2003058039A1 (fr) * 2001-12-29 2003-07-17 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Dispositif permettant d'actionner de maniere variable les soupapes de changement des gaz dans des moteurs a pistons alternatifs
DE10312961B3 (de) * 2003-03-24 2004-05-13 Thyssenkrupp Automotive Ag Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
GB2395229A (en) * 2002-11-16 2004-05-19 Mechadyne Plc Engine with variable valve lift and timing mechanism
WO2004085802A1 (fr) 2003-03-24 2004-10-07 Thyssenkrupp Automotive Ag Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type
WO2004085804A1 (fr) * 2003-03-24 2004-10-07 Thyssenkrupp Automotive Ag Dispositif de commande variable de soupapes d'echange des gaz pour moteurs a combustion interne et procede de fonctionnement d'un dispositif de ce type
GB2403770A (en) * 2003-06-30 2005-01-12 Christopher Paulet Mel Walters I.c. engine valve gear
JP2005214199A (ja) * 2004-01-28 2005-08-11 Man B & W Diesel Gmbh 内燃機関の吸排気弁用弁駆動装置
US6932035B1 (en) 2005-01-28 2005-08-23 Ford Global Technologies, Llc Cylinder valve operating system for internal combustion engine
EP1605142A1 (fr) * 2003-03-11 2005-12-14 Yamaha Hatsudoki Kabushiki Kaisha Mecanisme de soupape variable pour moteur a combustion interne
FR2872542A1 (fr) * 2004-07-05 2006-01-06 Renault Sas Dispositif d'actionnement variable d'au moins une soupape de moteur a combustion interne et procede de commande associe
WO2006121181A1 (fr) * 2005-05-11 2006-11-16 Toyota Jidosha Kabushiki Kaisha Dispositif de commande variable de soupape
WO2006136125A1 (fr) * 2005-06-17 2006-12-28 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Mecanisme de commande de soupapes pour moteurs a combustion interne
FR2890692A1 (fr) * 2005-09-14 2007-03-16 Renault Sas Dispositif d'actionnement variable d'au moins une soupape de moteur a combustion interne pour vehicule automobile et procede de commande associe
US7363899B2 (en) 2006-02-22 2008-04-29 Schaeffler Kg Valve drive of an internal combustion engine
EP1923546A1 (fr) * 2005-09-08 2008-05-21 HONDA MOTOR CO., Ltd. Dispositif de commande de soupape pour moteur
EP1985816A1 (fr) * 2007-03-05 2008-10-29 PIAGGIO & C. S.p.A. Système de variation continue du levage et de la phase des soupapes dans un moteur à combustion interne
EP2157292A1 (fr) * 2008-08-20 2010-02-24 Delphi Technologies, Inc. Ensemble de soupape d'échappement pour moteur à combustion interne
ITBO20090063A1 (it) * 2009-02-10 2010-08-11 Moto Morini S P A Dispositivo per il controllo dell'alzata di una valvola per un motore
CN103161543A (zh) * 2011-12-13 2013-06-19 常州嵘驰发动机技术有限公司 驱动装置、具有该驱动装置的内燃机和使用该内燃机的车辆
CN103184910A (zh) * 2012-12-20 2013-07-03 浙江吉利汽车研究院有限公司杭州分公司 连续可变气门升程装置
CN103925036A (zh) * 2013-01-15 2014-07-16 长城汽车股份有限公司 可变气门升程驱动装置
CN103925030A (zh) * 2013-01-15 2014-07-16 长城汽车股份有限公司 一种可变气门升程驱动装置
CN104088682A (zh) * 2014-06-30 2014-10-08 常州嵘驰发动机技术有限公司 驱动装置
US9281144B2 (en) 2012-02-09 2016-03-08 Siemens Aktiengesellschaft Circuit breaker contact assembly and cam lever
EP3173593A1 (fr) * 2015-11-26 2017-05-31 MAN Truck & Bus AG Commande de soupape variable comprenant un culbuteur
CN108194159A (zh) * 2018-02-07 2018-06-22 吉林大学 一种气门正时-升程调节机构
DE102017119348A1 (de) * 2017-08-24 2019-02-28 Man Truck & Bus Ag Variabler Ventiltrieb
CN110005496A (zh) * 2019-05-15 2019-07-12 杰锋汽车动力***股份有限公司 用于内燃机的两级可变气门升程机构
CN110295967A (zh) * 2019-06-28 2019-10-01 广汽三菱汽车有限公司 连续可变气门升程装置
CN112302754A (zh) * 2019-07-29 2021-02-02 舍弗勒技术股份两合公司 中间摇臂及气门摇臂***

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DE2629554A1 (de) * 1976-07-01 1978-01-12 Daimler Benz Ag Lastregelung fuer gemischverdichtende brennkraftmaschinen mit ventilsteuerung
FR2357731A1 (fr) * 1976-07-08 1978-02-03 Chrysler France Procede de commande d'ouverture des soupapes d'un moteur a combustion interne et dispositif pour la mise en oeuvre de ce procede
JPS6453009A (en) 1987-08-21 1989-03-01 Honda Motor Co Ltd Valve timing adjuster for engine
DE4243169C1 (de) * 1992-12-19 1994-05-26 Daimler Benz Ag Variable Ventilsteuerungseinrichtung
WO1994013935A1 (fr) * 1992-12-13 1994-06-23 Bayerische Motoren Werke Aktiengesellschaft Commande de soupape pour un moteur a combustion interne

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Publication number Priority date Publication date Assignee Title
DE2256093A1 (de) * 1972-11-16 1974-05-22 Daimler Benz Ag Ventilsteuerungseinrichtung fuer brennkraftmaschinen
DE2629554A1 (de) * 1976-07-01 1978-01-12 Daimler Benz Ag Lastregelung fuer gemischverdichtende brennkraftmaschinen mit ventilsteuerung
FR2357731A1 (fr) * 1976-07-08 1978-02-03 Chrysler France Procede de commande d'ouverture des soupapes d'un moteur a combustion interne et dispositif pour la mise en oeuvre de ce procede
JPS6453009A (en) 1987-08-21 1989-03-01 Honda Motor Co Ltd Valve timing adjuster for engine
WO1994013935A1 (fr) * 1992-12-13 1994-06-23 Bayerische Motoren Werke Aktiengesellschaft Commande de soupape pour un moteur a combustion interne
DE4243169C1 (de) * 1992-12-19 1994-05-26 Daimler Benz Ag Variable Ventilsteuerungseinrichtung

Cited By (68)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0761935A3 (fr) * 1995-09-01 1998-02-11 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Entraínement de soupape variable, en particulier pour moteurs à combustion interne
US5899180A (en) * 1995-09-01 1999-05-04 Bayerische Motoren Werke Aktiengesellschaft Variable valve gear, particularly for internal-combustion engines
EP0761935A2 (fr) * 1995-09-01 1997-03-12 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Entraînement de soupape variable, en particulier pour moteurs à combustion interne
EP0962629A2 (fr) 1998-06-05 1999-12-08 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Commande de soupape variable pour moteur à combustion interne
US6145485A (en) * 1998-06-05 2000-11-14 Bayerische Motoren Werke Aktiengesellschaft Variable valve operating mechanism for an internal combustion engine
WO2000008309A1 (fr) * 1998-08-05 2000-02-17 Delphi Technologies, Inc. Mecanisme variable de commande de soupapes
FR2799792A1 (fr) * 1999-10-15 2001-04-20 Jean Louis Rico Moteur thermique a distribution variable
GB2357131A (en) * 1999-12-09 2001-06-13 Mechadyne Internat Plc Valve actuating mechanism
EP1143119A3 (fr) * 2000-03-21 2003-01-29 Toyota Jidosha Kabushiki Kaisha Dispositif pour varier la phase et la course d'une soupape et appareil de contrôle de volume d'air d'admission
DE10036373A1 (de) * 2000-07-18 2002-02-14 Herbert Naumann Hubventilsteuerungen
DE10066054B4 (de) * 2000-07-18 2006-07-13 Thyssenkrupp Automotive Ag Hubventilsteuerung für Kraftmaschinen
WO2003008772A1 (fr) * 2001-07-17 2003-01-30 Thyssenkrupp Automotive Ag Commande variable de course de soupape
CN1322227C (zh) * 2001-07-17 2007-06-20 泰森克鲁普汽车股份公司 可变阀门行程控制装置
WO2003058039A1 (fr) * 2001-12-29 2003-07-17 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Dispositif permettant d'actionner de maniere variable les soupapes de changement des gaz dans des moteurs a pistons alternatifs
KR100953463B1 (ko) * 2001-12-29 2010-04-16 프라운호퍼-게젤샤프트 츄어 푀르더룽 데어 안게반텐 포르슝에.파우. 왕복 엔진 내의 가스 교환 밸브를 가변적으로 작동시키기위한 장치
US6997153B2 (en) 2001-12-29 2006-02-14 Fraunhofer Gesellschaft zur Förderung der angewandten Forschung e.V. Device for variably actuating the gas exchange valves in reciprocating engines
DE10164493B4 (de) * 2001-12-29 2010-04-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Vorrichtung zur variablen Betätigung der Ladungswechselventile in Hubkolbenmotoren
US6584943B1 (en) * 2002-09-18 2003-07-01 Daimlerchrysler Corporation Variable compound rocker system for push rod and overhead camshaft engines
US7117831B2 (en) 2002-11-16 2006-10-10 Mechadyne Plc Engine with variable lift valve mechanism
GB2395229A (en) * 2002-11-16 2004-05-19 Mechadyne Plc Engine with variable valve lift and timing mechanism
EP1605142A1 (fr) * 2003-03-11 2005-12-14 Yamaha Hatsudoki Kabushiki Kaisha Mecanisme de soupape variable pour moteur a combustion interne
EP1605142A4 (fr) * 2003-03-11 2010-08-04 Yamaha Motor Co Ltd Mecanisme de soupape variable pour moteur a combustion interne
WO2004085802A1 (fr) 2003-03-24 2004-10-07 Thyssenkrupp Automotive Ag Dispositif d'actionnement variable des soupapes d'echange des gaz de moteurs a combustion interne et procede permettant de faire fonctionner un dispositif de ce type
DE10312961B3 (de) * 2003-03-24 2004-05-13 Thyssenkrupp Automotive Ag Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
DE10312958B4 (de) * 2003-03-24 2005-03-10 Thyssen Krupp Automotive Ag Vorrichtung zur vairablen Betätigung der Gaswechselventile von Verbrennungsmotoren und Verfahren zum Betreiben einer derartigen Vorrichtung
DE10312959B4 (de) * 2003-03-24 2006-10-05 Thyssenkrupp Automotive Ag Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
WO2004085804A1 (fr) * 2003-03-24 2004-10-07 Thyssenkrupp Automotive Ag Dispositif de commande variable de soupapes d'echange des gaz pour moteurs a combustion interne et procede de fonctionnement d'un dispositif de ce type
DE10312961C5 (de) * 2003-03-24 2009-01-29 Thyssenkrupp Presta Teccenter Ag Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren
GB2403770A (en) * 2003-06-30 2005-01-12 Christopher Paulet Mel Walters I.c. engine valve gear
CN100439662C (zh) * 2004-01-28 2008-12-03 曼·B及W柴油机公开股份有限公司 用于内燃机的气体交换阀的气门传动装置
DE102004004179A1 (de) * 2004-01-28 2005-08-25 Man B & W Diesel Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
JP2005214199A (ja) * 2004-01-28 2005-08-11 Man B & W Diesel Gmbh 内燃機関の吸排気弁用弁駆動装置
FR2872542A1 (fr) * 2004-07-05 2006-01-06 Renault Sas Dispositif d'actionnement variable d'au moins une soupape de moteur a combustion interne et procede de commande associe
US6932035B1 (en) 2005-01-28 2005-08-23 Ford Global Technologies, Llc Cylinder valve operating system for internal combustion engine
US7591238B2 (en) 2005-05-11 2009-09-22 Toyota Jidosha Kabushiki Kaisha Variable valve-operating device
WO2006121181A1 (fr) * 2005-05-11 2006-11-16 Toyota Jidosha Kabushiki Kaisha Dispositif de commande variable de soupape
WO2006136125A1 (fr) * 2005-06-17 2006-12-28 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Mecanisme de commande de soupapes pour moteurs a combustion interne
US7748356B2 (en) 2005-06-17 2010-07-06 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Valve train for internal combustion engines
EP1923546A1 (fr) * 2005-09-08 2008-05-21 HONDA MOTOR CO., Ltd. Dispositif de commande de soupape pour moteur
EP1923546A4 (fr) * 2005-09-08 2009-12-30 Honda Motor Co Ltd Dispositif de commande de soupape pour moteur
US7779797B2 (en) 2005-09-08 2010-08-24 Honda Motor Co., Ltd. Engine valve operating system
FR2890692A1 (fr) * 2005-09-14 2007-03-16 Renault Sas Dispositif d'actionnement variable d'au moins une soupape de moteur a combustion interne pour vehicule automobile et procede de commande associe
US7363899B2 (en) 2006-02-22 2008-04-29 Schaeffler Kg Valve drive of an internal combustion engine
EP1985816A1 (fr) * 2007-03-05 2008-10-29 PIAGGIO & C. S.p.A. Système de variation continue du levage et de la phase des soupapes dans un moteur à combustion interne
EP2157292A1 (fr) * 2008-08-20 2010-02-24 Delphi Technologies, Inc. Ensemble de soupape d'échappement pour moteur à combustion interne
ITBO20090063A1 (it) * 2009-02-10 2010-08-11 Moto Morini S P A Dispositivo per il controllo dell'alzata di una valvola per un motore
CN103161543B (zh) * 2011-12-13 2017-09-05 常州嵘驰发动机技术有限公司 驱动装置、具有该驱动装置的内燃机和使用该内燃机的车辆
CN103161543A (zh) * 2011-12-13 2013-06-19 常州嵘驰发动机技术有限公司 驱动装置、具有该驱动装置的内燃机和使用该内燃机的车辆
US9281144B2 (en) 2012-02-09 2016-03-08 Siemens Aktiengesellschaft Circuit breaker contact assembly and cam lever
CN103184910A (zh) * 2012-12-20 2013-07-03 浙江吉利汽车研究院有限公司杭州分公司 连续可变气门升程装置
CN103925030A (zh) * 2013-01-15 2014-07-16 长城汽车股份有限公司 一种可变气门升程驱动装置
CN103925036A (zh) * 2013-01-15 2014-07-16 长城汽车股份有限公司 可变气门升程驱动装置
CN103925036B (zh) * 2013-01-15 2017-02-08 长城汽车股份有限公司 可变气门升程驱动装置
CN104088682A (zh) * 2014-06-30 2014-10-08 常州嵘驰发动机技术有限公司 驱动装置
CN104088682B (zh) * 2014-06-30 2018-12-18 常州嵘驰发动机技术有限公司 驱动装置
EP3173593A1 (fr) * 2015-11-26 2017-05-31 MAN Truck & Bus AG Commande de soupape variable comprenant un culbuteur
CN107035452A (zh) * 2015-11-26 2017-08-11 曼卡车和巴士股份公司 带有摇动杆的可变的阀传动机构
US20170152769A1 (en) * 2015-11-26 2017-06-01 Man Truck & Bus Ag Variable valve drive having a rocker lever
US10436079B2 (en) 2015-11-26 2019-10-08 Man Truck & Bus Ag Variable valve drive having a rocker lever
RU2724811C2 (ru) * 2015-11-26 2020-06-25 Ман Трак Унд Бас Аг Изменяемый клапанный привод и транспортное средство с таким клапанным приводом
CN107035452B (zh) * 2015-11-26 2021-10-08 曼卡车和巴士股份公司 带有摇动杆的可变的阀传动机构
DE102017119348A1 (de) * 2017-08-24 2019-02-28 Man Truck & Bus Ag Variabler Ventiltrieb
US10619527B2 (en) 2017-08-24 2020-04-14 Man Truck & Bus Ag Variable valve train
CN108194159A (zh) * 2018-02-07 2018-06-22 吉林大学 一种气门正时-升程调节机构
CN108194159B (zh) * 2018-02-07 2023-10-10 吉林大学 一种气门正时-升程调节机构
CN110005496A (zh) * 2019-05-15 2019-07-12 杰锋汽车动力***股份有限公司 用于内燃机的两级可变气门升程机构
CN110295967A (zh) * 2019-06-28 2019-10-01 广汽三菱汽车有限公司 连续可变气门升程装置
CN112302754A (zh) * 2019-07-29 2021-02-02 舍弗勒技术股份两合公司 中间摇臂及气门摇臂***

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