Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
  • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
  • F16F15/14—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers
  • F16F15/1407—Suppression of vibrations in rotating systems by making use of members moving with the system using masses freely rotating with the system, i.e. uninvolved in transmitting driveline torque, e.g. rotative dynamic dampers the rotation being limited with respect to the driving means
  • F16F15/145—Masses mounted with play with respect to driving means thus enabling free movement over a limited range

Definitions

• the present invention relates to a reciprocating internal combustion engine comprising means for reducing acyclicism for low speed operations.
• a first solution is to stop the engine at red lights and then restart it. This requires coupling an engine-alternator directly to the crankshaft, which is expensive.
• the second solution consists in reducing the speed of rotation of the engines at idle.
• the acyclism increases, which makes its operation unstable.
• the only method to decrease acyclism is to increase the moment of inertia of the steering wheel.
• this has many disadvantages, namely: a penalizing increase in the mass of the powertrain; a necessary increase in starter performance; and a reduction in engine performance, the speed increases of which become slower.
• the arrangement according to the present invention makes it possible to simultaneously obtain two results which are antagonistic, namely: a steering wheel which has a large moment of inertia for acyclism, which greatly reduces this, and a moment of inertia more weak for the engine because we use a flywheel whose mass is weaker.
• pendulum masses are used associated either with the flywheel or with a pulley at the other end of the crankshaft.
• these pendulum systems are not used to protect the crankshaft against a risk of rupture due to vibrations, but to combat the effects due to moment of inertia of the engine assembly (crankshaft and pistons) when the latter rotates at low speed (that is to say when the crankshaft is subjected to very low loads), and is therefore subject to acyclisms.
• Such pendulum systems are described in US Patent 5,295,411.
• the pendulum will be tuned on the number of explosions per revolution and this for speeds close to that of the idle (700 rev / min and below), therefore for a low operation charge.
• the pendulums are tuned on harmonic 2.
• the pendulums are therefore tuned on the harmonic of acyclism or, at the very least, in the vicinity of the pulsation of its major harmonic.
• ⁇ is the speed of average rotation of the motor, we know that during operation, the instantaneous speed varies between ⁇ , and ⁇ 2 ; the coefficient of irregularity
• n I ⁇ , - ⁇ -, I; we can calculate that for an engine
• pendulum element (s), suitably tuned, compensates for acyclism.
• the dimensioning and the mass of the pendulum elements are advantageously chosen as well as their positioning on the flywheel so as to tune them to the major harmonics of acyclism. It can be seen that, in this way, it is possible to run, for example, a 4-cylinder, 4-stroke engine at average speeds close to 300 rpm without annoying irregularities and with a flywheel lightened compared to those of l 'state of the art.
• the present invention therefore relates to an internal combustion engine, the crankshaft of which is provided, for example, with a flywheel, characterized in that said flywheel is provided with at least one pendulum element whose dimensioning, mass and positioning on said flywheel are determined so as to be in the vicinity of the pulsation of the major harmonic (s) of acyclism.
• the major acyclic harmonic has a pulsation equal to twice the speed of rotation.
• the present invention may also include the following arrangements, taken separately or in combination: a) the flywheel is provided with at least two housings in which a flyweight can move freely; b) the flywheel is provided with three housings arranged at 120 ° from one another; c) the flywheel is provided with two groups of three housings arranged at 120 ° from one another, the two groups being symmetrically interposed and each group having different dimensions and positions as well as different masses; d) the side walls of each housing are flat and separated from each other by a raceway, the counterweight being a roller capable of rolling between the sidewalls on the raceway; preferably, the roller is a cylinder of revolution; e) the raceway of the housing, against which the roller rolls, is a surface of revolution about an axis perpendicular to the side walls of the housing; f) the housing can be a cylinder of revolution; g) the cross section of the raceway by a plane parallel to the side walls of the housing is a curve determined by calculation as a function of the desired
• the moving mass has a T-section; m) the moving mass has a U-shaped section; n) the single pendulum system is constituted by an asymmetrical counterweight carried pivotally by an axis; o) the single pendulum system consists of a cylindrical counterweight provided on one side with holes, these holes can be separated or combined in a single light; p) the single pendulum system consists of a sealed housing filled with two immiscible liquids of different densities, for example oil and mercury; q) the single pendulum system consists of a toothed pinion meshing either on a central pinion or on a peripheral toothing; r) the pendulum system, either single or two-wire, is blocked beyond a predetermined speed of rotation by radial slides each retained by a spring moving under the effect of centrifugal force; s) the pendulum system consists of n weights arranged at n / 360 ° from each other, these weights having the shape of a circular sector whose
• FIG. 1 shows an axial sectional view, along I-I of Figure 2, of the end of the crankshaft of an engine according to the invention provided with a flywheel with pendulum elements;
• FIG. 2 shows an elevational view, partially broken away, of the steering wheel of Figure 1, along II-II of Figure 1;
• Figures 3 and 4 show an elevational view and an axial sectional view of an alternative embodiment of Figures 1 and 2;
• FIG. 11 shows an elevational view of a second alternative embodiment of the steering wheel of Figures 1 and 2;
• FIG. 12 shows an elevational view of a third alternative embodiment of the steering wheel of Figures 1 and 2;
• FIG. 13 shows an elevational view of a fourth alternative embodiment of the steering wheel of Figures 1 and 2;
• FIG. 14 shows an elevational view of a fifth alternative embodiment of the steering wheel of Figures 1 and 2;
• - Figure 15 shows an elevational view of a sixth alternative embodiment of Figures 1 and 2;
• FIG. 16 shows an elevational view of a seventh alternative embodiment of Figures 1 and 2;
• FIG. 17 shows an elevational view of an eighth alternative embodiment of Figures 1 and 2;
• FIG. 18 shows an elevational view of an alternative embodiment of the systems described in Figures 7 and 9, incorporating locking means similar to those of Figure 17;
• FIG. 19 shows a plan view of a fourth embodiment of the present invention, with a variant shown in dotted lines;
• FIG. 20 is a perspective view of Figure 19.
• a sleeve 3 on which is fixed coaxially a flywheel inertia designated by the general reference 4. This fixing is carried out by means of eight studs 46 regularly distributed around the axis of the flywheel 4.
• the flywheel 4 is constituted by a solid disc 40 of a sufficiently large thickness to have a significant moment of inertia adapted to the engine with which it is associated.
• This disc 40 is pierced with three circular openings 41 at 120 ° from one another, in each of which is inserted a cylindrical ring 42.
• the two faces of the disc 40 are covered by annular flanges 43 which are fixed to the disc 40 by screws 47 cooperating with threaded bores 48 of the disc 40.
• These two flanges 43 cover the ends rings 42 and define with the internal volume of each cylindrical ring 42 a closed cylindrical housing 44.
• each housing 44 is disposed a counterweight constituted by a roller 45.
• This roller 45 is a solid cylinder whose length is substantially equal (and in fact slightly less) to the thickness of the disc 40; this distance is that which separates the two flanges 43 and therefore defines the length of the housing 44. It follows that the rollers 45 can move freely in their housings 44 and, in particular, roll along the internal wall of said housings 44.
• each of the rollers 45 rests at the bottom of its housing 44; as soon as the engine reaches a few revolutions per minute, for example at the starter drive speed, the rollers 45 come to occupy, under the effect of centrifugal force, the radial position shown in FIGS. 1 and 2.
• rollers 45 When the engine idles, acyclisms appear, which result in successions of decelerations and accelerations of the rotation of the crankshaft 1: the rollers 45 then roll in one direction or the other along the wall of their cylindrical housings, which counterbalances, or at the very least decreases, said acyclisms, said rollers then behaving like pendular elements.
• housings 44 are cylindrical, so that each roller 45 can be considered as a pendulum; but the invention is not limited to this particular case.
• each housing can be arbitrary: circular (as shown), elliptical, or other; it may not even be symmetrical with respect to the radius of the disc 40 passing through the center of the cross section: this makes it possible to modify at will the reaction law of the flyweights on acyclic phenomena.
• each roller 45 does not cross the entire thickness of the flywheel 40 but is hollowed out in the latter over only part of this thickness.
• Each housing 44 is provided with a rolling ring 42 which projects partially out of the housing 44 and is covered by a cover 49.
• the roller 45 struggles in the cylindrical volume formed by the bottom 44a of the housing 44, the ring 42 and the cover 49.
• Figures 5 and 6 show a second embodiment of the device according to the invention, the elements identical to those of Figures 1 to 4 bearing the same references.
• This second embodiment is characterized in that the flywheel 4 comprises two groups of three housings regularly interposed between them.
• each housing 44 is arranged at 120 ° from one another, each housing comprising a counterweight 45.
• Each housing 54 is provided with a rolling ring 52, a counterweight 55 and is closed by a cover 59. It should be noted that all the dimensional parameters of the housing 54 are different from those of the housing 44, namely: their distance from center of the flywheel 40 is smaller, their diameter is smaller and the mass of the flyweight 55 different.
• Figures 7 to 10 illustrate a third embodiment of the invention.
• the flywheel 4 has a peripheral groove 60.
• the portions 61a of three masses 61 in the shape of a T, are arranged, arranged at 120 ° from one another .
• Each portion 61a of a mass 61 is provided with two circular holes 62.
• the flywheel 40 is pierced with three pairs of circular holes 63, arranged at 120 ° from one another.
• Each pair of holes 63 corresponds to the two holes 62 of a mass 61.
• the holes 62 and 63 are crossed by axes 64.
• the axes 64 have a diameter smaller than that of the holes 62 and 63.
• Each mass 61 then constitutes the equivalent of a pendulum held by two wires.
• each mass 61 oscillates in one direction then in the other.
• dimensions, position and mass are determined by mathematical calculation so that they are tuned to a pulsation close to the pulsation of the chosen harmonic, in this case the major harmonic of l of the engine under consideration.
• FIGs 9 and 10 illustrate an alternative embodiment of the device of Figures 7 and 8, the shape of each mass being inverted and U-shaped so as to make a stirrup; identical elements bearing the same references.
• Each mass 71 is a part whose section is U-shaped so as to cover the flywheel 40.
• each mass 71 is provided with two side walls 70 whose spacing is slightly greater than the thickness of the steering wheel 40.
• the side walls 70 are provided with holes 72, which correspond to the holes 62 in Figures 7 and 8; the steering wheel 40 is provided with the same holes 63 as in FIGS. 7 and 8 and axes 74 (corresponding to axes 64) pass through holes 63 and 72.
• FIG. 11 shows various alternative embodiments which have been designed to prevent the weights or rollers from sliding.
• the rollers 45 moving freely in cylindrical housings 44 are replaced by asymmetrical weights constituting the pendular mass 80 mounted on an axis 81 disposed in the center O of the housing 44 so as to be able to pivot in a housing 82.
• the counterweight 80 is constituted by a cylinder which can rotate freely inside the housing 82 by virtue of a ball bearing 83. Holes 83 all arranged on the same side of the diameter 85 have the effect to bring up a asymmetry in the mass of the counterweight 80, thus constituting the pendulum mass.
• FIG. 13 it can be seen that the three holes 83 in FIG. 12 have been brought together in a single semi-circular lumen 83a.
• Figure 14 we see that in the cylindrical housing
• a tight cylindrical case 86 is also placed, also of center O, this tight case 86 being filled by means of two liquids of different densities and immiscible, for example, oil 87 and mercury 88. Under the effect of centrifugal force, the mercury forms a kind of lens 88 as shown and constitutes the pendulum mass.
• housing 82 is internally provided with a serration on which meshes a pinion
• FIG. 16 represents a reverse arrangement to that of FIG. 15.
• the pinion 89 forming a pendular mass, meshes on the centered axis 81a which is toothed.
• the toothed axis 81a can be fixed or pivotally mounted on its axis O.
• Figures 17 and 18 show arrangements which make it possible to cancel the effect of pendulum masses from a certain speed; whether with a single pendulum (figure 17) or a bi-wire pendulum (figure 18).
• FIG 17 corresponds to Figure 2 and the same elements have the same references.
• the circular openings 41 formed in the flywheel 40 are arranged cylindrical rings
• the slide 90 can move in a housing 91 whose axis is radial.
• a tension spring 92 keeps the slider 90 in contact with the bottom 91a of the housing 91.
• the slide 90 moves radially against the spring 92.
• the slide 90 has a curved surface 93, intended to constitute a seat for the roller 45.
• the ring 42 has an appropriate opening to allow passage to slide 90.
• the pieces occupy the positions shown in dashed lines: that is to say that the slide 90 is in abutment on the bottom 91a of its housing 91 and that the roller 45 can move freely.
• the roller comes to take the position shown in solid lines and then plays the pendulum role assigned to it according to the present invention. From a certain speed of rotation, defined as a function of the mass of the slider 90 and the resistance of the spring 92, the slider 93 blocks the roller 45 which then becomes inoperative.
• FIG. 18 represents a locking system playing the same role as that of FIG. 17, but for a bi-wire pendulum system, such as that of FIGS. 7 and 8.
• the same elements as those of FIGS. 7 and 8 have the same references and are not described again.
• the device comprises four bi-wired pendulum masses 61 arranged at 90 ° from one another (instead of three at 120 °).
• the flywheel 40 comprises four radial housings 91, at 90 ° from one another, the axes of these housings 91 coinciding with the axes of symmetry of said flywheel 40 separating the four bi-wire pendulum masses 61.
• each housing 91 slides a slide 90, against a traction resort 92; but the end 94 of the slide has a wedge shape at a 90 ° angle instead of being a semi-cylindrical seat 93.
• each slider 90 When stopped, each slider 90 rests against the bottom 91a of its housing 91 under the effect of its tension spring 92. It is only from a speed determined as a function of the mass of each slider 90 and the resistance of its spring 92 that the slides 90 will slide under the effect of centrifugal force to block the masses 61, which then become inoperative.
• Figures 19 and 20 show a fourth embodiment of the invention. Referring to these figures, it can be seen that the pendulum masses are constituted by six weights 100, each weight 100 being pivotally mounted on the flywheel 40 by means of an axis 101 and a bearing or bearing 102. The axes 101 are arranged at 60 ° from each other and the weights 100 have the shape of a circular sector whose angle at the center is 60 °.
• the pins 101 are carried by a circular flange 103.
• each counterweight can have a bore 104, centered on its bisector, disposed beyond the axis 101 relative to the center of the flywheel 40, in which a moving mass
• the invention is not limited to the case where there are six weights, the number "n" weights may be any, but preferably greater than 3.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Acoustics & Sound (AREA)
• Aviation & Aerospace Engineering (AREA)
• Mechanical Engineering (AREA)
• Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
• Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
• Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Applications Claiming Priority (3)

Publications (1)

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Family Applications (1)

Country Status (8)

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• 1999
  • 1999-10-04 KR KR1020017015117A patent/KR20020022054A/ko not_active Application Discontinuation
  • 1999-10-04 WO PCT/FR1999/002357 patent/WO2000073678A1/fr not_active Application Discontinuation
  • 1999-10-04 EP EP99946284A patent/EP1181466A1/fr not_active Withdrawn
  • 1999-10-04 MX MXPA01012008A patent/MXPA01012008A/es unknown
  • 1999-10-04 JP JP2001500140A patent/JP2003500618A/ja active Pending
  • 1999-10-04 CN CN99816665A patent/CN1350621A/zh active Pending
  • 1999-10-04 BR BR9917323-9A patent/BR9917323A/pt not_active Application Discontinuation
• 2000
  • 2000-05-23 AR ARP000102497A patent/AR024065A1/es unknown

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