JP2008151152A - Conversion method between linear/rotational motion of reciprocal engine - Google Patents

Conversion method between linear/rotational motion of reciprocal engine Download PDF

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JP2008151152A
JP2008151152A JP2004347582A JP2004347582A JP2008151152A JP 2008151152 A JP2008151152 A JP 2008151152A JP 2004347582 A JP2004347582 A JP 2004347582A JP 2004347582 A JP2004347582 A JP 2004347582A JP 2008151152 A JP2008151152 A JP 2008151152A
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connecting rod
internal gear
rotational motion
force
output shaft
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Hiroshi Morikawa
洋 森川
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Priority to JP2004347582A priority Critical patent/JP2008151152A/en
Priority to PCT/JP2005/020330 priority patent/WO2006049268A1/en
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    • 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
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • 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
    • F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than 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
    • F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
    • F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
    • F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
    • F16H19/043—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack for converting reciprocating movement in a continuous rotary movement or vice versa, e.g. by opposite racks engaging intermittently for a part of the stroke

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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)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To perform conversion from linear motion to rotational motion more efficiently in a reciprocal engine. <P>SOLUTION: In a crank mechanism, an internal gear having an oblong, or ellipsoidal shape, or a shape similar to them is provided in place of a bearing for a crank shaft on a large end of a connecting rod. An external gear coupled to an output shaft is made into internal contact with the internal gear, and force for performing linear reciprocating motion in a longitudinal direction of the internal gear at a small end of the connecting rod is converted into force for rotational motion. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

内燃機関に代表される往復直線運動を回転運動に変換して使用する機械全般。
［背景技術］
従来から往復直線運動を回転運動に変える方法は、ピニオンとラックの組み合わせとクランク機構の二つに大別されてきた。General machines that use reciprocating linear motion represented by internal combustion engines converted to rotational motion.
[Background technology]
Conventionally, the method of changing the reciprocating linear motion into the rotational motion has been roughly divided into a combination of a pinion and rack and a crank mechanism.

そしてピニオンとラックの組み合わせにおいては、運動部分の機械摩擦を除けばラックの直線運動の仕事量は、全てピニオンの回転運動の仕事量に変換される。しかしながら、往と復とでピニオンを同じ方向に連続して回転させるには、ピニオンをラックから切り離すか、あるいは空転させておこなってきた。ピニオンの同一方向えの滑らかな回転運動への変換は出来ないのである。  In the combination of the pinion and the rack, all the work of the linear motion of the rack is converted into the work of the rotational motion of the pinion except for the mechanical friction of the moving part. However, in order to continuously rotate the pinion in the same direction between forward and backward, the pinion has been separated from the rack or idled. The pinion cannot be converted into a smooth rotational motion in the same direction.

一方クランク機構はよく知られているように運動の変換を滑らかに、かつ、連続的におこなわれる。しかし、回転力に関与する直線方向の力はクランク機構の上死点においては０であり、以下、クランク角π／２ラヂアンにおいて１．０下死点のπラヂアンで０となる図 １ に示すｓｉｎカーブとなる。クランク角０ラヂアンからπラヂアンまでの回転に関与する力の全仕事量は、ｓｉｎカーブに囲まれた斜線の面積になる。そしてピニオンとラックの組み合わせにおいては，当該する面積はＯａｂπとなりその面積比は π 対
２ となる。π−２≒１．１４に相当する仕事量が、従来は使われていなかった。On the other hand, as is well known, the movement of the crank mechanism is performed smoothly and continuously. However, the linear force involved in the rotational force is 0 at the top dead center of the crank mechanism, and is 0 thereafter at a crank angle of π / 2 radians at 1.0 bottom dead center of π radians as shown in FIG. It becomes a sin curve. The total work amount of the force involved in the rotation from the crank angle of 0 radians to π radians is the area of the oblique line surrounded by the sin curve. In the combination of pinion and rack, the area concerned is Oabπ, and the area ratio is π: 2. A work amount corresponding to π−2≈1.14 has not been used conventionally.

直線運動を回転運動に変換することではピニオンとラックの組み合わせのほうがπ／２倍だけクランク機構より効率が良い。しかしこれは直線運動の力が上死点から下死点まで同じ大きさのときで、実際のレシプロ機関において内圧は、上死点を過ぎてからクランク角約２０度で最高となり、以下急激に減少しπ／２ではその半分以下となり、下死点よりかなり前で０となることを考えれば、変換効率の差はさらに大きくなる。
［発明の開示］
［発明が解決しようとする課題］
ピニオンとラックの組み合わせにおいて、ピニオンがその始動点から直線運動をおこないラックの長さのの限界で反転し滑らかに、かつ、連続的に、始動点に戻れるようにし、直線往復運動から回転運動への変換効率をクランク機構に比べて高くなるようにする。
［課題を解決するための手段］By converting linear motion to rotational motion, the combination of pinion and rack is more efficient than the crank mechanism by π / 2 times. However, this is when the linear motion force is the same from top dead center to bottom dead center. In an actual reciprocating engine, the internal pressure reaches its maximum at a crank angle of about 20 degrees after passing top dead center. The difference in conversion efficiency is further increased considering that it decreases and becomes less than half of it at π / 2 and becomes zero well before the bottom dead center.
[Disclosure of the Invention]
[Problems to be solved by the invention]
In the combination of pinion and rack, the pinion moves linearly from its starting point and reverses at the limit of the rack length so that it can return smoothly and continuously to the starting point. The conversion efficiency is made higher than that of the crank mechanism.
[Means for solving problems]

内歯歯車と外歯歯車の組み合わせにおいて、内歯歯車を長円形または楕円形になし一部分をラック状にする。そしてこれを、コネクチングロッドの大端部におく。外歯歯車は出力軸につながっている。次に小端部はピストンピンによって往復直線運動のみおこなうのでコネクチングロッドの動きを規制しないと、歯車同士が噛み合わなくなる。そこで、コネクチングロッドのどの部分でもよいが、１つまたは複数個のピンを出力軸に平行に設け、歯車同士が常に噛み合うように、あらかじめ定めた軌跡を持つ溝にこのピンを差し込む。以下図面によって説明する。なおピンの数は１つとして説明する。  In the combination of the internal gear and the external gear, the internal gear is formed into an oval or an ellipse and a part thereof is formed into a rack shape. This is then placed at the large end of the connecting rod. The external gear is connected to the output shaft. Next, since only the reciprocating linear motion is performed at the small end portion by the piston pin, the gears do not mesh unless the movement of the connecting rod is restricted. Therefore, although any part of the connecting rod may be used, one or a plurality of pins are provided in parallel to the output shaft, and these pins are inserted into grooves having a predetermined locus so that the gears are always engaged with each other. This will be described below with reference to the drawings. The description will be made assuming that the number of pins is one.

１はコネクチングロッドで小端部にはピストンピン孔があり、この部分は矢印の方向に上下し、直線運動をおこなう。大端部は長円形・楕円形あるいはそれに類する形状の内歯歯車２となっている。３は出力軸につながる外歯歯車、４はガイドピンである。これはコネクチングロッドの、どの部分にあってもよいが、説明では最下端にもうけている。５はガイド溝で４のガイドピンと対をなしており、その形状は、歯車が外れないようにコネクチングロッドのガイドピンが矢印のように連続して滑らかに動くように規制している。反対方向も可である。６はコネクチングロッドが出力軸方向にぶれないようにコネクチングロッドの両側に設ける案内壁である。本説明では、５のガイド溝は６に設けられているが、各々べつにもうけてもよい。
［発明の効果］Reference numeral 1 denotes a connecting rod having a piston pin hole at a small end portion, and this portion moves up and down in the direction of an arrow to perform linear motion. The large end portion is an internal gear 2 having an elliptical shape, an elliptical shape, or the like. 3 is an external gear connected to the output shaft, and 4 is a guide pin. This can be at any part of the connecting rod, but in the description it is at the bottom end. Reference numeral 5 denotes a guide groove which is paired with the guide pin 4 and its shape restricts the guide pin of the connecting rod so as to continuously and smoothly move as indicated by an arrow so that the gear does not come off. The opposite direction is also possible. Reference numeral 6 denotes guide walls provided on both sides of the connecting rod so that the connecting rod does not shake in the output shaft direction. In this description, 5 guide grooves are provided in 6, but may be provided in each.
[The invention's effect]

ピストンの往復直線運動の力をクランク機構より効率よく回転運動に変換できる。結果として回転力・出力が上がり、燃費がよくなる。  The reciprocating linear motion force of the piston can be converted into rotational motion more efficiently than the crank mechanism. As a result, the rotational force / output increases and fuel efficiency improves.

クランク機構におけるコネクチングロッドの反力によって生ずるピストンの側面の振動、いわゆるピストンスラップ発生を抑える。雑音が減る。また、ピストンリングの気密性が上昇する。  It suppresses the occurrence of so-called piston slap generation on the side surface of the piston caused by the reaction force of the connecting rod in the crank mechanism. Noise is reduced. In addition, the airtightness of the piston ring is increased.

クランクの回転半径の２倍とピストン行程は同じ長さだから、機械の幅はこれより大きくなるが、本発明では、それに該当する値は、出力軸の歯車半径を内歯歯車の幅から、引いた値となる。また、コネクチングロッドの長さは、クランクの回転半径より長いので、本発明の内歯歯車の内側の長さは当然ピストン行程と同じ値となるから、ピストンの運動方向の寸法も小さくなり、機械全体の大きさを小型化できる。  The width of the machine is larger than this because the piston stroke is twice as long as the rotation radius of the crank, but in the present invention, the value corresponding to that is subtracting the gear radius of the output shaft from the width of the internal gear. Value. In addition, since the length of the connecting rod is longer than the rotation radius of the crank, the internal length of the internal gear of the present invention is naturally the same value as the piston stroke. The overall size can be reduced.

本発明では、ピストンの行程とクランクの回転半径は、関係なくなるので大行程のものを自由に設計できる。大型のヂィーゼルでは有利なことである。  In the present invention, since the stroke of the piston and the radius of rotation of the crank are not related, the stroke of the large stroke can be designed freely. This is advantageous for large diesels.

直列に配置した多気筒エンジンでは、従来はクランク軸にねじり振動が発生しするので、気筒数には限界があった。しかし、本発明では工作が難しく、高価なクランク軸そのものが必要ないので設計の自由度が増すことになる。  In a multi-cylinder engine arranged in series, the number of cylinders has been limited because torsional vibration is generated on the crankshaft. However, in the present invention, it is difficult to work, and an expensive crankshaft itself is not necessary, so that the degree of freedom in design increases.

圧縮行程のポンプ効率が良くなる。  The pump efficiency of the compression stroke is improved.

従来のレシプロ機関ではピストンの最高圧力はクランク角２０度（このときの回転に関与する垂直方向の分力は約．０．３４である）の近辺にあった。これをもっと上死点側に動かすことができる。
［発明を実施するための最良の形態］
従来から設計され作られているクランク機構を、本発明の内歯歯車形式に置き変えれば、より小型軽量で、出力の大きい燃費の少ないレシプロ機関が製造できる。In the conventional reciprocating engine, the maximum pressure of the piston is in the vicinity of a crank angle of 20 degrees (the vertical component force involved in the rotation at this time is about .0.34). You can move this closer to top dead center.
[Best Mode for Carrying Out the Invention]
Replacing a conventionally designed and made crank mechanism with the internal gear type of the present invention makes it possible to manufacture a reciprocating engine that is smaller and lighter and has a large output and low fuel consumption.

はラックとピニオンの組み合わせと、クランク機構の直線運動を回転運動に変換させるときの仕事量の効率をしめす長方形とｓｉｎ曲線である。Is a combination of a rack and a pinion, and a rectangle and a sin curve that indicate the work efficiency when converting the linear motion of the crank mechanism into rotational motion. は直線往復運動を回転運動に変換させる装置の射影図である。FIG. 5 is a projection view of an apparatus for converting linear reciprocating motion into rotational motion.

符号の説明Explanation of symbols

１はコネクチングロッド、２は内歯歯車、３は外歯歯車、４はガイドピン、５はガイド溝、６は案内壁である。1 is a connecting rod, 2 is an internal gear, 3 is an external gear, 4 is a guide pin, 5 is a guide groove, and 6 is a guide wall.

Claims (4)

クランク機構において、コネクチングロッドの大端部にあるクランクシャフト用の軸受けの代わりに、長円形・楕円形またはそれに類似する内歯歯車を設け、これに出力軸につながった外歯歯車を内接させて、内歯歯車の長手方向にコネクチングロッドの小端部で直線往復運動をおこなう力を回転運動の力に変換させる機構。  In the crank mechanism, instead of the bearing for the crankshaft at the large end of the connecting rod, an oval or elliptical internal gear is provided, and an external gear connected to the output shaft is inscribed in it. A mechanism for converting the force of linear reciprocation at the small end of the connecting rod in the longitudinal direction of the internal gear into the force of rotational motion. 長円形・楕円形またはそれに類似する内歯歯車を大端部側にもったコネクチングロッド。  Connecting rod with oval / elliptical or similar internal gear on the large end side. ［請求項 ２］におけるコネクチングロッドが、その内歯歯車と対になる外歯歯車の二つが常に接する動きをするように、あらかじめ定めた軌跡を描く運動をおこなうように規制するコネクチングロッドに設けたガイドピン、およびその対となるガイド溝。  The connecting rod according to [Claim 2] is provided on the connecting rod for restricting the movement so as to draw a predetermined trajectory so that two of the external gears paired with the internal gear always move in contact with each other. A guide pin and a pair of guide grooves. ［請求項 ２］におけるコネクチングロッドが、運動中に出力軸の長手方向にぶれるのを防ぐ案内壁の設置。  Installation of a guide wall that prevents the connecting rod in [Claim 2] from shaking in the longitudinal direction of the output shaft during movement.
JP2004347582A 2004-11-01 2004-11-01 Conversion method between linear/rotational motion of reciprocal engine Pending JP2008151152A (en)

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JP2004347582A JP2008151152A (en) 2004-11-01 2004-11-01 Conversion method between linear/rotational motion of reciprocal engine
PCT/JP2005/020330 WO2006049268A1 (en) 2004-11-01 2005-10-31 Mutual conversion method between linear/rotational motion of reciprocal engine

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Cited By (3)

* Cited by examiner, † Cited by third party
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JP2016517824A (en) * 2013-05-08 2016-06-20 ゲンデル，アレキサンダー Gear and lever transmission system and method
JPWO2022202843A1 (en) * 2021-03-24 2022-09-29
JP7224704B1 (en) 2022-09-20 2023-02-20 中山 善隆 internal combustion engine

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CN113915100B (en) * 2021-11-03 2024-02-20 芜湖欧宝机电有限公司 Assembling method of compressor with gear mechanism driving piston

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
JPS54135968A (en) * 1978-04-13 1979-10-22 Kazuji Matsuoka Motion converter

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016517824A (en) * 2013-05-08 2016-06-20 ゲンデル，アレキサンダー Gear and lever transmission system and method
JPWO2022202843A1 (en) * 2021-03-24 2022-09-29
WO2022202843A1 (en) * 2021-03-24 2022-09-29 善▲隆▼ 中山 Internal combustion engine
JP7224704B1 (en) 2022-09-20 2023-02-20 中山 善隆 internal combustion engine
WO2024062841A1 (en) * 2022-09-20 2024-03-28 善▲隆▼ 中山 Internal combustion engine
JP2024044203A (en) * 2022-09-20 2024-04-02 中山 善隆 internal combustion engine

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