WO1990012202A1 - Moteur a mouvement alternatif avec deux mecanismes a manivelle - Google Patents

Moteur a mouvement alternatif avec deux mecanismes a manivelle Download PDF

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Publication number
WO1990012202A1
WO1990012202A1 PCT/JP1989/000357 JP8900357W WO9012202A1 WO 1990012202 A1 WO1990012202 A1 WO 1990012202A1 JP 8900357 W JP8900357 W JP 8900357W WO 9012202 A1 WO9012202 A1 WO 9012202A1
Authority
WO
WIPO (PCT)
Prior art keywords
crank
shaft
flywheel
spring
stage
Prior art date
Application number
PCT/JP1989/000357
Other languages
English (en)
Japanese (ja)
Inventor
Mitsugu Aoyama
Original Assignee
Mitsugu Aoyama
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 Mitsugu Aoyama filed Critical Mitsugu Aoyama
Priority to PCT/JP1989/000357 priority Critical patent/WO1990012202A1/fr
Publication of WO1990012202A1 publication Critical patent/WO1990012202A1/fr

Links

Classifications

    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/04—Engines with prolonged expansion in main cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • 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
    • F16H—GEARING
    • F16H21/00—Gearings comprising primarily only links or levers, with or without slides
    • F16H21/10—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane
    • F16H21/16—Gearings comprising primarily only links or levers, with or without slides all movement being in, or parallel to, a single plane for interconverting rotary motion and reciprocating motion
    • F16H21/18—Crank gearings; Eccentric gearings
    • F16H21/22—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric
    • F16H21/28—Crank gearings; Eccentric gearings with one connecting-rod and one guided slide to each crank or eccentric with cams or additional guides

Definitions

  • the present invention relates to a reciprocating engine in an internal combustion engine, and converts the combustion explosion of fuel gas into torque from a crank connecting shaft to a crank shaft from a piston via a connector.
  • the conventional engine's crank connecting train, the crank, and the crank mechanism composed of the crank shaft are combined with the latter-stage crank mechanism.
  • the pre-stage crank mechanism is combined with the post-stage crank mechanism so that it is rotated simultaneously with the rotation of the post-stage crank shaft, and the explosion starter is controlled.
  • the crank connecting shaft of the front crank mechanism operates by advancing, and the reverse crank or frame does not receive reverse or braking force. Without generating, the strong first explosive motive power, And conversion of the rotary DOO / Lek force values as one likes, to provide a highly efficient energy saving Rugie Nji down.
  • the crank connecting shaft to receive the force is The direction of the force from the mouth can be received only in the direction of 90 degrees which is different from the direction of the side:
  • the explosive motive force is the highest in such a connection mechanism between the crank and the crank. Even if it does, it will not be a trek to rotate the crank shaft, but the explosive power of the starting force obtained by burning the precious fuel oil will be ended as an invalid tonnolek. However, before the invalid tonnolek is reduced to the effective tonnolec, the crank connection axis continues from the top dead center of the crank to the position where the crank connecting shaft has rotated about 15 degrees in the rotation direction. is there.
  • the cause of the low efficiency that occurs in the present invention is that the crank mechanism of the engine is used as it is, as a subsequent crank mechanism, and further added to the subsequent crank mechanism, so that the former crank mechanism is accumulated.
  • the mechanism by unions are those was Unishi'll be operated as a two-stage click rank mechanism c
  • the force from the con- tract mouth is analyzed by a solidtle analysis, and the explosion activating force is the first occurrence.
  • the value of 50 kg / ci is assumed to be 50, and that 50 cannot be transmitted about 5 ⁇ , and cannot be moved.
  • the two-stage crank mechanism which consists of a book and a second stage, is intended to solve the damage of (1). 1 to 5, the embodiment will be described.
  • the rear crank mechanism is the same as the conventional one.]
  • the front-stage crank mechanism is installed in parallel with the rear-stage crank mechanism.
  • the configuration is such that the front rank I 3 uses the front rank fulcrum $ fl l4 at the bottom, the lower rank and the flywheel 12 at the bottom, and the bottom dead center position.
  • Each shaft is set at about 25 degrees to the direction, and both ends of the front crank connecting shaft 9 are fixed above the front crank 13 with new paper.
  • the inner ring of the roller—bearing 8 having the same inner diameter as the shaft diameter of the preceding crank connecting shaft 9 is attached.
  • the outer ring of the bearing 8 is clamped by the curved member of the crank joint 7 of the connector, and tightened with a nut and a nut.
  • the upper part of the connector 6 is combined with the piston 4 and is installed through the screw pin 5.
  • a circular hole 27 is drilled in the axial direction.]
  • the rear-stage crank connecting shaft 10 penetrates into the circular-hole 27, Both ends of the ⁇ 10 are fixed to the upper part of the rear crank / fly wheel 12, respectively.
  • the spring receiving hole W formed near the center of the hoist 12 is set to correspond to the spring rear receiving portion W that forms the hole.
  • crank shaft spring receiving shaft 24 is supported via a spring TO push meter 21 and a spring job meter / lens 20.
  • This work -3 ⁇ 43 is — eyes ⁇ 3 ⁇ 4 Even if the crank connection shaft 9 and the rear-stage crank connection shaft 10 rotate to reach the top dead center position of the crank], even if the combustion explosion reaches the maximum value 15 degrees before, It does not act to reverse or brake the crank 11, but rather acts to accelerate and increase rotation.
  • the direction of the hole length of the cutout hole 27 is such that the front rank 13 moves the front rank connection shaft 9 of the upper part with the front rank fulcrum shaft I 4 as a fulcrum.
  • the rear-stage crank connecting shaft 10 having a shaft diameter equal to the inner diameter of the circular cutout hole 27 slides in the hole.
  • the rear crank connecting shaft is always located on the right side in the round hole 27 except during the explosion.
  • an imaginary point 16 where the explosive motive force is concentrated is located from the piston pin center point 28 to the preceding crank fulcrum ball W.
  • the force from the piston 4 is that the front crank connecting shaft 9 and the rear crank connecting shaft 10 are at the top dead center.
  • the maximum value of the waterfall reaches the maximum through connector 6, and even if it reaches intensely, it does not reverse the previous crank connecting shaft 9 and rotates forward. , And induces a side-bending operation on the front crank connected glaze 9, which is the center axis. This will be referred to as "intermediate shaft lateral bending operation".
  • the upward and downward explosive forces coming from piston 4 correspond to the downward acting force of the preceding crank connecting shaft 9, and the force is further reduced to the former crank supporting shaft I.
  • the front crank connecting shaft is converted to a rightward moving force.
  • the preceding click rank I 3 is of letting YokoUtsuri ⁇ , in this case, is provided in the central portion of the front click rank 13
  • front click rank scan pre ring bearing shaft 24 is simultaneously moved Then, the lateral movement force boosts the spring 22 due to the action of the roller, and presses the spring 22 downward and to the right. It shrinks.
  • the formula for calculating the mass of the second stage crank fly wheel 12 and the connectors and bistonni used in the present invention is the same as the conventional formula)).
  • Yo! It is necessary to double the calculated amount. Therefore, by increasing the weight of the rear crank flywheel 12, the inertia and acceleration of the rear crank flywheel 12 are increased even if the rear crank flywheel 12 is rotating.
  • the starting force of the combustion explosion instantaneously generates a large force, and the force is rapidly transmitted to crank 13 via connector 6 at this time.
  • the front crank fulcrum shaft M which received the starting force applied in the vertical direction, takes its own fulcrum and does not have a position. The direction in which the force acts is converted into 90 degrees different lateral rotation!
  • the front click rank connecting shaft 9 is laterally folded by receiving, the force may not move the front click rank I 3
  • the front crank spring receiving shaft 24 provided there serves to further compress the spring 22, so that the mosquito corresponds to the spring 22 and the front crank spring
  • the receiving shaft 24 is a floating fulcrum, and the fulcrum, which floats on the spring, and the force of the roller acting on the fulcrum, which jumps the front crank fulcrum shaft W in the rotational direction.
  • the rear crank and flywheel 12 on which the fulcrum shaft 14 is provided are started and rotated in the rotational direction, so that the rear crank 11 can be easily rotated. It causes rotation.
  • Fig. 5 is the result of the fact that the front crank connecting shaft 9 turned sideways, causing the rear crank connecting shaft 10 to inertially leave lor? And shift to the left.
  • the preceding crank fulcrum axis M is also I 4 .
  • the roller bearing 8 is also 8 '. 1 ( ⁇ is the rotation trajectory of the rear-stage crank connecting shaft 10.
  • I 4 the front-stage crank fulcrum shaft w that has received the “spring-up fulcrum swing-up operation” is used as the rear-stage crank and flare. This is the retreat position after rotating and moving Iho Inore 1.
  • the former rank 13 is 13.
  • the spring 22 used is in the shape of a core, but this is replaced by a plate-like one. is there.
  • Fig. 6, lower left! Tighten the lower contact spring plate 31 indicated by the dotted hatching to the left side of the lower contact spring plate attachment 32 with a bolt / let 35, and the lower contact panel attachment 32 with the Bonoreto 34. Then, it is fixed on the outer side of each of the rear-stage crank and flywheels 12.
  • the right part of the lower backing spring plate 31 is made to correspond to the front crank spring receiving shaft 2.
  • the upper contact spring plate 36 indicated by the 9-dot oblique line is tightened to the upper contact spring plate mounting member 37 with a bolt 40.
  • the contact spring plate attachment 37 is also fixed to the rear crank and flywheel 12 by attaching the bolt 38 to it.
  • the lower abutting the spring plate fitting 32 there is a curved surface portion 33, a right end portion of the lower abutting spring plate 31, front Kura ink split ring bearing shaft 2, and displaced by receiving the movement of the front Class tank I 3,
  • the back surface thereof comes in contact with the lower backing spring plate mounting device 32, and the back contact portion thereof follows the arc shape of the curved surface portion 33 of the lower backing spring plate mounting device 32. And move in the upper right direction.
  • the lower backing spring plate 31 moves a large distance from the top to the bottom when the explosion starting force from the piston 4 is weak against the movement of the front crank spring receiving shaft 24.
  • the lower contact spring plate 31 moves to the right in response to the further applied force from that portion, and the lower contact panel plate is substantially short and elastically elastic. It exerts the same effect as when it is made stronger, with the front crank spring receiving shaft having 24 forces; even if further starting force is applied from that part, the distance of its movement decreases in a sequential manner.
  • the upper spring plate 36, together with the lower spring plate 31 strongly sandwiches the front spring receiving shaft 24 from above and below, and the front crank 13 and the rear crank / flywheel 12 It is designed to maintain flexibility in mutual dynamic movements between the two. 4 1 in the sixth figure, bored to the rear dunk rank and off La Lee Ho Lee Norre 12 ⁇ is a circle cut-out large hole 4 1.
  • the elastic action of the lower and upper spring plates 31 and 36 is performed by using a semi-circular comb spring plate 30 made of artificial rubber and having an appropriate thickness.
  • upper spring mounting hole 17, lower spring charging hole, and rear spring receiving hole 19] 9 is fitted into the drilled shaft receiving hole 26
  • the front crank spring receiving shaft 24 penetrates through the center of the comb spring plate 30 to form new paper. Through. -.
  • the rear crank connecting shaft is located at a position where the pressure is high and about 20 degrees before the top dead center position immediately before the transition from the compression stroke to the explosion issuance, Even if the explosive power due to ignition reaches the maximum pressure, the first stage crank 13 elasticity 3 ⁇ 4 The second stage crank and flywheel 12 reverses or rebounds due to the occurrence of “intermediate shaft side bending : operation”. Without receiving the braking action, the entire explosive motive force is dissipated in the direction of the main rotation in the forward direction, so as to further accelerate and rotate. In this way, the elastic operation of the "middle shaft side-bending operation" can be smoothly performed by the sexual response of the first-rank crank spring 24 and the spring 22. "Spring up operation of sprung fulcrum".
  • FIG. 9 is an explanatory diagram showing “intermediate shaft lateral bending work ⁇ ” and “spring-up fulcrum M” generated between the i-rank 12 and the rear crank # 11. If the numbers in the figures are described by name, the following? S i? Is common to each figure.
  • Tightening bolt 38 mounting spring plate mounting bracket 37 to be attached to the upper spring plate mounting bracket 37, rear crank spring ⁇ 1 for the front crank spring receiving shaft 24 drilled in the flywheel 1 to shift.
  • Large circular hole 41 which is the common symbol for each of the above.
  • the engine crank suspension structure is made into a two-stage crank structure consisting of a front stage and a rear stage, and is operated side by side on the same shaft, so that "the intermediate shaft machine folding operation” and “the 'Rotating operation', the 'high explosive power of the explosive energy', which was almost completely eliminated by the invalid energy It can be converted to torque and taken out as a rotating output, so that a conventional engine can inhale fuel and generate fuel, and it can obtain an output increase about twice that of the generated horsepower.
  • So-new paper When used in all power sources, the engine consumes half the amount of fuel oil to provide the horsepower needed by the device]) and is a highly efficient engine.
  • this invention engine By equipping automobiles around the world with this invention engine, it is possible to use only about half a year of fuel oil, even if it is now a major social problem and the air pollution caused by nitrogen oxides in exhaust gas In particular, by reducing the amount of exhaust gas to less than half, it is possible to achieve harmless values that are below the standard value, and the fossil fuel slope resources will save a great deal of the world.
  • incorporating this invention engine into the diesel engine will reduce the power consumption of the large-scale railway by increasing the amount of oil used by the railway. be able to.
  • the current boiler-fired thermal power generation can also be used to generate electricity at a low-cost, large-scale diesel-powered facility, so that the price of the electric wire can be reduced.
  • halving the amount of fuel to be consumed can be reduced by a large amount of ⁇ , and the profit margin can be increased.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transmission Devices (AREA)

Abstract

Un mécanisme à manivelle arrière se compose d'un vilebrequin arrière (11) servant d'arbre de sortie de moteur, d'une manivelle arrière servant également de roue libre (12), et d'un arbre de liaison de manivelle arrière (10). Une manivelle avant (13) est disposée sur le côté interne de la manivelle arrière servant également de roue libre (12) et une partie inférieure de la manivelle avant (13) est soutenue rotative sur la manivelle arrière servant également de roue libre (12) à proximité d'un point mort bas par l'intermédiaire d'un arbre d'articulation de manivelle avant (14), une partie supérieure de la manivelle avant (13) étant pourvue dans un arbre de liaison de manivelle avant (9) d'un passage elliptique (27), dans lequel un arbre de liaison de manivelle arrière (10) est introduit avec du jeu, une partie de liaison de manivelle (7) d'une bielle (10) étant soutenue pivotante autour de l'arbre de liaison de manivelle avant (9) par l'intermédiaire d'un roulement à rouleaux (8). La manivelle avant (13) reçoit une force de compression de la part d'un ressort (22), qui est placé dans une partie réceptrice (19) sur un côté arrière d'un passage d'introduction de ressort ménagé dans la manivelle arrière (12), par l'intermédiaire d'un roulement à ressort avant (24), et elle se trouve dans la position de l'arbre de liaison de manivelle avant représenté dans la figure 1. Grâce à l'utilisation des deux mécanismes à manivelle décrits ci-dessus, la force de démarrage s'exerçant vers le bas lors de l'explosion peut être récupérée comme force latérale de l'arbre de liaison de manivelle avant (9) et ensuite comme force rotative de la manivelle avant (13). Ainsi, cette force de démarrage lors de l'explosion peut être convertie efficacement en une force de démarrage rotative.
PCT/JP1989/000357 1989-04-04 1989-04-04 Moteur a mouvement alternatif avec deux mecanismes a manivelle WO1990012202A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP1989/000357 WO1990012202A1 (fr) 1989-04-04 1989-04-04 Moteur a mouvement alternatif avec deux mecanismes a manivelle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP1989/000357 WO1990012202A1 (fr) 1989-04-04 1989-04-04 Moteur a mouvement alternatif avec deux mecanismes a manivelle

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992007200A1 (fr) * 1990-10-20 1992-04-30 Un Kil Paek Mecanisme de transmission de puissance a bielle/vilebrequin
WO1994019590A1 (fr) * 1993-02-26 1994-09-01 Mitsugu Aoyama Moteur alternatif dote d'un mecanisme a manivelle a deux etages
FR2900703A1 (fr) * 2006-05-05 2007-11-09 Peugeot Citroen Automobiles Sa Dispositif de liaison entre un vilebrequin et des bielles

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5637066Y2 (fr) * 1976-05-20 1981-08-31
JPS5773801A (en) * 1980-08-25 1982-05-08 Jiyon Bii Jiima Internal combustion engine
JPS6055742U (ja) * 1983-09-22 1985-04-18 三菱自動車工業株式会社 エンジン

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5637066Y2 (fr) * 1976-05-20 1981-08-31
JPS5773801A (en) * 1980-08-25 1982-05-08 Jiyon Bii Jiima Internal combustion engine
JPS6055742U (ja) * 1983-09-22 1985-04-18 三菱自動車工業株式会社 エンジン

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992007200A1 (fr) * 1990-10-20 1992-04-30 Un Kil Paek Mecanisme de transmission de puissance a bielle/vilebrequin
WO1994019590A1 (fr) * 1993-02-26 1994-09-01 Mitsugu Aoyama Moteur alternatif dote d'un mecanisme a manivelle a deux etages
FR2900703A1 (fr) * 2006-05-05 2007-11-09 Peugeot Citroen Automobiles Sa Dispositif de liaison entre un vilebrequin et des bielles

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