JPH09125981A - Direct-coupled assembly of internal combustion engine and driven machinery - Google Patents
Direct-coupled assembly of internal combustion engine and driven machineryInfo
- Publication number
- JPH09125981A JPH09125981A JP7284934A JP28493495A JPH09125981A JP H09125981 A JPH09125981 A JP H09125981A JP 7284934 A JP7284934 A JP 7284934A JP 28493495 A JP28493495 A JP 28493495A JP H09125981 A JPH09125981 A JP H09125981A
- Authority
- JP
- Japan
- Prior art keywords
- internal combustion
- combustion engine
- planetary gear
- sun gear
- piston
- 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.)
- Granted
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
- 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
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
-
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/24—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type
- F02B75/246—Multi-cylinder engines with cylinders arranged oppositely relative to main shaft and of "flat" type with only one crankshaft of the "pancake" type, e.g. pairs of connecting rods attached to common crankshaft bearing
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transmission Devices (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、内燃機関のピスト
ンに直結して、コンプレッサのピストンを始めとする各
種直線往復移動体を駆動するようにしたものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention is directly connected to a piston of an internal combustion engine and drives various linear reciprocating bodies including a piston of a compressor.
【０００２】[0002]
【従来の技術】クランク装置は、内燃機関やコンプレッ
サ等において往復運動と回転運動間で動力変換を行なう
装置として周知であるが、ピストンとクランク軸を連結
する連接棒がピストン上死点及び下死点以外では常にシ
リンダ軸線に対して傾斜していることから動力変換効率
の上で無駄があるし、連接棒から反作用としてピストン
が受ける横方向分力でシリンダの内壁を擦るいわゆるピ
ストンスラップが生じ、これが振動、騒音、磨耗などの
原因となっている。2. Description of the Related Art A crank device is well known as a device for converting power between reciprocating motion and rotary motion in an internal combustion engine, a compressor or the like. However, a connecting rod connecting a piston and a crank shaft has a piston top dead center and a bottom dead center. Except for the points, it is always inclining with respect to the cylinder axis, which is wasteful in terms of power conversion efficiency. This causes vibration, noise, and wear.
【０００３】しかし、内燃機関を動力源としてコンプレ
ッサのピストンなど直線往復移動可能な移動体を有する
被駆動機械を駆動しようとする場合、従来のクランク装
置の利用は避けることができない。図４は内燃機関Ｅと
コンプレッサＣの３種類の結合態様を示したもので、図
４（ａ）と（ｂ）は内燃機関ＥとコンプレッサＣのいず
れもクランク装置を具備するもので、（ａ）はプーリ５
０ａ，５０ｂとベルト５１で回転運動を伝達し、（ｂ）
はカップリング５２で回転運動を伝達している。また図
４（ｃ）はエンジンＥとコンプレッサＣのシリンダ軸線
の交差部に共通のクランク装置５３を配設し、内燃機関
ＥとコンプレッサＣでクランクピン５４を共通にしたも
のである。However, when trying to drive a driven machine having a moving body capable of linearly reciprocating movement such as a piston of a compressor by using an internal combustion engine as a power source, it is inevitable to use a conventional crank device. FIG. 4 shows three types of coupling modes of the internal combustion engine E and the compressor C, and FIGS. 4 (a) and 4 (b) show that both the internal combustion engine E and the compressor C have a crank device. ) Is pulley 5
0a, 50b and the belt 51 transmit the rotational motion, (b)
Transmits the rotational movement by the coupling 52. Further, FIG. 4C shows that a common crank device 53 is arranged at the intersection of the cylinder axes of the engine E and the compressor C, and the internal combustion engine E and the compressor C have a common crank pin 54.
【０００４】[0004]
【発明が解決しようとする課題】以上３つの結合方式の
いずれもクランク装置を利用していることから、動力変
換にかなりの無駄が生じてしまう。このような従来のク
ランク装置の課題を解決するため、本願発明者らは新し
い発想に基づく新型のクランク装置を先に提案した（特
願平６−１２１７７６号）。この新型クランク装置は、
連接棒とクランク軸との間に遊星歯車機構を介装するこ
とによって、クランク軸の回転に伴う連接棒下端の横方
向の振幅を遊星歯車機構で吸収するようにしている。こ
れによって連接棒は常にシリンダ軸線上を傾斜揺動する
ことなく上下動し、動力変換効率が向上し、ピストンス
ラップも解消される。Since all of the above three coupling systems use the crank device, a considerable waste of power conversion occurs. In order to solve such a problem of the conventional crank device, the inventors of the present application previously proposed a new crank device based on a new idea (Japanese Patent Application No. 6-121776). This new crank device
By interposing the planetary gear mechanism between the connecting rod and the crankshaft, the lateral amplitude of the lower end of the connecting rod due to the rotation of the crankshaft is absorbed by the planetary gear mechanism. As a result, the connecting rod always moves up and down on the cylinder axis without tilting and swinging, improving power conversion efficiency and eliminating piston slap.
【０００５】本発明の目的は、この新型クランク装置を
応用して、内燃機関のピストンにコンプレッサのピスト
ン等の各種直線往復移動体を直結し、効率的な動力伝達
を行なわせることにある。An object of the present invention is to apply this new type crank device to directly connect various linear reciprocating movable bodies such as a piston of a compressor to a piston of an internal combustion engine to efficiently transmit power.
【０００６】[0006]
【課題を解決するための手段】前記課題を解決するため
本発明の内燃機関と被駆動機械の直結型組立体は、一直
線上に互いに整合して配設された、直線往復移動可能な
ピストンを有する内燃機関及び直線往復移動可能な移動
体を有する被駆動機械と、前記内燃機関と被駆動機械の
中間位置の前記一直線上に中心Ｏを有し固定的に配設さ
れた内周太陽歯車と、前記内周太陽歯車と噛合して自転
及び公転可能であって、前記内周太陽歯車のピッチ円直
径の二分の一のピッチ円直径を有する遊星歯車と、前記
遊星歯車の中心部を自転可能に支持する腕部と、前記遊
星歯車の公転を許容するように前記中心Ｏの回りに回転
自在な軸部とを有するクランク部材と、前記内燃機関の
ピストンと前記被駆動機械の移動体との間で前記一直線
に沿って延在し、前記ピストンと移動体を前記遊星歯車
の外周部分に枢支連結する連接棒とを有する。In order to solve the above-mentioned problems, a direct-coupling type assembly of an internal combustion engine and a driven machine according to the present invention comprises linearly reciprocating pistons arranged in alignment with each other. A driven machine having the internal combustion engine and a movable body capable of linear reciprocating movement, and an inner peripheral sun gear fixedly arranged with a center O on the straight line at an intermediate position between the internal combustion engine and the driven machine. , A planetary gear having a pitch circle diameter which is ½ of the pitch circle diameter of the inner periphery sun gear and capable of rotating and revolving by meshing with the inner periphery sun gear, and capable of rotating the center portion of the planet gear. A crank member having an arm portion supported by a shaft member and a shaft portion rotatable around the center O so as to allow the planetary gear to revolve, a piston of the internal combustion engine, and a moving body of the driven machine. Extending along the straight line between The serial piston and mobile and a connecting rod pivotally connected to the outer peripheral portion of the planetary gear.
【０００７】本発明の組立体では、振動を防止し動力伝
達効率をよりよくするために、遊星歯車の中心部回りの
静的および動的重量バランスと、クランク部材の軸部回
りの静的および動的重量バランスをとることが重要であ
る。In the assembly of the present invention, in order to prevent vibration and improve power transmission efficiency, the static and dynamic weight balance around the center of the planetary gear and the static and dynamic weight around the shaft of the crank member are performed. Dynamic weight balancing is important.
【０００８】また本発明の組立体をコンパクトに構成す
るために、内周太陽歯車の内側空間であって、遊星歯車
を除く空間にクランク部材の腕部を回転自在に収容する
ことが有効である。In order to make the assembly of the present invention compact, it is effective to rotatably accommodate the arm portion of the crank member in the inner space of the inner sun gear except for the planetary gears. .
【０００９】本発明に係る内燃機関と被駆動機械の直結
型組立体において内燃機関を駆動すると、内燃機関のピ
ストンの直線往復動力が連接棒を介して被駆動機械の移
動体に直接に伝達され、移動体がピストンとまったく同
じように直線往復動する。従って従来のクランク装置の
ようなピストンスラップ分力は生じない。このとき遊星
歯車は、内周太陽歯車に沿って自転しつつ公転し、この
公転に伴いクランク部材が回転される。このクランク部
材は遊星歯車を自転自在かつ公転自在に支持するだけで
あって、特別な負荷はかけられていない。従ってピスト
ンから移動体への動力伝達効率がきわめて高くなる。ま
た、遊星歯車の公転慣性とクランク部材の回転慣性によ
りフライホイール効果が生まれ、内燃機関のピストンお
よび被駆動機械の移動体の上下両死点からの下降および
上昇がスムーズに行なわれる。When the internal combustion engine and the driven machine according to the present invention are directly connected, the linear reciprocating power of the piston of the internal combustion engine is directly transmitted to the moving body of the driven machine through the connecting rod. , The moving body reciprocates linearly just like a piston. Therefore, the piston slap component force unlike the conventional crank device is not generated. At this time, the planetary gear revolves along the inner sun gear while rotating about its axis, and the crank member is rotated along with this revolution. This crank member only supports the planetary gears so that they can rotate and revolve freely, and no special load is applied. Therefore, the power transmission efficiency from the piston to the moving body becomes extremely high. Further, the flywheel effect is produced by the revolution inertia of the planetary gears and the rotation inertia of the crank member, so that the piston of the internal combustion engine and the moving body of the driven machine can be smoothly lowered and raised from both upper and lower dead points.
【００１０】[0010]
【発明の実施の形態】以下に本発明を内燃機関−コンプ
レッサ組立体１に適用した実施形態を図１〜図３に基づ
いて説明する。この組立体１は内燃機関Ｅのピストン２
ａの直線往復動を、そのままコンプレッサＣ（被駆動機
械）のピストン２ｂ（移動体）に伝達して直線往復動さ
せるようにしたものである。このため内燃機関Ｅのシリ
ンダ４ａとコンプレッサＣのシリンダ４ｂは、各軸線が
一直線となるように整合して配設されている。また内燃
機関Ｅのピストン２ａとコンプレッサＣのピストン２ｂ
は、連接棒６で一体に連結されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment in which the present invention is applied to an internal combustion engine-compressor assembly 1 will be described below with reference to FIGS. This assembly 1 is a piston 2 of an internal combustion engine E.
The linear reciprocating motion of a is transmitted as it is to the piston 2b (moving body) of the compressor C (driven machine) for linear reciprocating motion. Therefore, the cylinder 4a of the internal combustion engine E and the cylinder 4b of the compressor C are arranged so that their axes are aligned with each other. Also, the piston 2a of the internal combustion engine E and the piston 2b of the compressor C
Are connected together by a connecting rod 6.
【００１１】内燃機関ＥとコンプレッサＣの中間部に
は、それぞれのシリンダ４ａ，４ｂの整合軸線上に中心
Ｏを定めた内周太陽歯車８ａが固定的に配設されてい
る。この内周太陽歯車８ａには、そのピッチ円直径の半
分のピッチ円直径の遊星歯車１０が噛合され、この遊星
歯車８の周縁部側面に一致して配設された軸部１２に連
接棒６の中間部が結合されている。この軸部１２は、遊
星歯車１０に回転自在に配設すれば連接棒６とは固定結
合でよいし、また軸部１２を連接棒６に回転自在に枢支
させれば軸部１２は遊星歯車１０に固定配設してよい。
なお、連接棒６上における軸部１２の位置は、組立体１
をコンパクトに構成するために通常は連接棒６の長さの
丁度中間位置であるが、連接棒６のいずれか一端にやや
寄せて配設することも可能である。また連接棒６は一体
物とする他、組み立て誤差等を吸収する目的で軸部１２
の部分で分離し、一方のピストン２ａと軸部１２を第１
連接棒で連結し、他方のピストン２ｂと軸部１２を第２
連接棒で連結する構成としてもよい。An inner peripheral sun gear 8a, whose center O is defined on the alignment axis of the cylinders 4a and 4b, is fixedly disposed in the intermediate portion between the internal combustion engine E and the compressor C. A planetary gear 10 having a pitch circle diameter half the pitch circle diameter is meshed with the inner peripheral sun gear 8a, and a connecting rod 6 is attached to a shaft portion 12 arranged so as to match the peripheral side surface of the planetary gear 8. The middle parts of are joined together. The shaft portion 12 may be fixedly connected to the connecting rod 6 if the shaft portion 12 is rotatably arranged on the planetary gear 10. Alternatively, if the shaft portion 12 is rotatably supported by the connecting rod 6, the shaft portion 12 is a planet. It may be fixedly arranged on the gear 10.
The position of the shaft portion 12 on the connecting rod 6 is determined by the assembly 1
In order to make the structure compact, it is usually at the intermediate position of the length of the connecting rod 6, but it is also possible to dispose it at one end of the connecting rod 6 slightly closer to it. Further, the connecting rod 6 is formed as an integral body, and the shaft portion 12 is used for the purpose of absorbing an assembly error or the like.
And separate one piston 2a and the shaft 12 into the first
Connect it with a connecting rod, and connect the other piston 2b and shaft 12 to the second
It may be configured to be connected by a connecting rod.
【００１２】遊星歯車１０の中心部は、図３のように、
内周太陽歯車８ａの中心Ｏ位置に軸部１４ａを定めたク
ランク部材１４の腕部１４ｂの先端部に回転自在に支持
されている。このクランク部材１４は図１ないし図３で
紙面に垂直な方向に延在しており、遊星歯車１０を内周
太陽歯車８ａの内側で自転自在かつ公転自在に支持して
いる。The central portion of the planetary gear 10 is, as shown in FIG.
The inner peripheral sun gear 8a is rotatably supported at the tip of an arm portion 14b of the crank member 14, which defines a shaft portion 14a at a position O. The crank member 14 extends in a direction perpendicular to the plane of the drawing in FIGS. 1 to 3, and supports the planetary gear 10 inside the inner peripheral sun gear 8a so as to be rotatable and revolvable.
【００１３】内燃機関−コンプレッサ組立体１の基本構
造は以上の通りであるが、これを図２に基づいてさらに
具体的に説明する。図２は内周太陽歯車８ａと遊星歯車
１０からなる遊星歯車機構１６を連接棒６の左右に一対
で配設したものである。遊星歯車機構１６を連接棒６の
片側だけに配設してもよいが、このように遊星歯車機構
１６を左右一対で配設することにより、機械的な安定度
が格段に高まる。内燃機関Ｅのシリンダ４ａとコンプレ
ッサＣのシリンダ４ｂとの間に、円筒部１８ａを有する
ハウジング１８が配設され、このハウジング１８の内周
部に太陽歯車部材８の外周部が固定嵌合されている。The basic structure of the internal combustion engine-compressor assembly 1 is as described above, which will be described in more detail with reference to FIG. In FIG. 2, a pair of planetary gear mechanisms 16 including an inner peripheral sun gear 8a and a planetary gear 10 are arranged on the left and right of the connecting rod 6. The planetary gear mechanism 16 may be arranged only on one side of the connecting rod 6, but by arranging the planetary gear mechanism 16 in a left-right pair in this way, the mechanical stability is significantly improved. A housing 18 having a cylindrical portion 18a is disposed between the cylinder 4a of the internal combustion engine E and the cylinder 4b of the compressor C, and the outer peripheral portion of the sun gear member 8 is fixedly fitted to the inner peripheral portion of the housing 18. There is.
【００１４】太陽歯車部材８はリング状をなし、その内
周部片側に内周太陽歯車８ａが形成されている。この内
周太陽歯車８ａには、そのピッチ円直径の半分のピッチ
円直径の遊星歯車１０が自転自在かつ公転自在に噛合さ
れている。遊星歯車１０は反対側の遊星歯車と屈曲軸部
２０を介して一体連結されており、この屈曲軸部２０の
中間に形成された軸部１２に、連接棒６の中間部に形成
された軸孔２２が回転自在に枢支され、さらに連接棒６
の両端には、ピストンピン２４ａ，２４ｂによってピス
トン２ａ，２ｂが取付けられている。なお、屈曲軸部２
０から軸部１２と反対側で半径方向外方に延在して釣合
錘Ｍ１が一体形成されている。The sun gear member 8 has a ring shape, and an inner peripheral sun gear 8a is formed on one side of the inner peripheral portion thereof. A planetary gear 10 having a pitch circle diameter that is half the pitch circle diameter is meshed with the inner peripheral sun gear 8a in a freely rotatable and revolvable manner. The planetary gear 10 is integrally connected to the planetary gear on the opposite side via a bending shaft portion 20, and a shaft portion 12 formed in the middle of the bending shaft portion 20 is connected to a shaft formed in the middle portion of the connecting rod 6. The hole 22 is rotatably supported, and the connecting rod 6
Pistons 2a and 2b are attached to both ends of the piston by piston pins 24a and 24b. The bending shaft 2
A counterweight M1 is integrally formed so as to extend radially outward from 0 on the side opposite to the shaft portion 12.
【００１５】太陽歯車部材８の内周部には、クランク部
材１４を回転自在に支持するため、内周太陽歯車８ａに
隣接した軸受２６が形成されている。クランク部材１４
は内周太陽歯車８ａの内側空間にあって遊星歯車１０を
取り囲むように配設され、クランク部材１４の片側外周
が軸受２６によって回転自在に支持されている。クラン
ク部材１４の反対側外周はハウジング１８の内周に形成
された別の軸受２８で回転自在に支持されている。A bearing 26 is formed on the inner peripheral portion of the sun gear member 8 so as to rotatably support the crank member 14 and adjacent to the inner peripheral sun gear 8a. Crank member 14
Is arranged in the inner space of the inner peripheral sun gear 8a so as to surround the planetary gear 10, and one outer periphery of the crank member 14 is rotatably supported by a bearing 26. The outer periphery of the crank member 14 on the opposite side is rotatably supported by another bearing 28 formed on the inner periphery of the housing 18.
【００１６】遊星歯車１０の中心には油孔を兼ねた軸孔
３０が形成され、この軸孔３０にクランク部材１４から
突設された支軸部１４ｃが回転自在に嵌合されている。
遊星歯車１０に隣接する屈曲軸部２０の外周は、クラン
ク部材１４に形成された軸受１４ｄによって回転自在に
支持されている。なお、クランク部材１４から腕部１４
ｂと反対側で半径方向外方に延在して釣合錘Ｍ２が一体
形成されている。A shaft hole 30 also serving as an oil hole is formed at the center of the planetary gear 10, and a support shaft portion 14c protruding from the crank member 14 is rotatably fitted in the shaft hole 30.
The outer circumference of the bending shaft portion 20 adjacent to the planetary gear 10 is rotatably supported by a bearing 14d formed on the crank member 14. In addition, from the crank member 14 to the arm portion 14
A counterweight M2 is integrally formed to extend outward in the radial direction on the side opposite to b.
【００１７】前記釣合錘Ｍ１，Ｍ２について説明する
と、まずＭ１は遊星歯車１０の軸孔３０を中心とする静
的および動的重量バランス（すなわち遊星歯車１０の自
転重量バランス）をとるためのものであって、図３のよ
うに遊星歯車１０の中心から釣合錘Ｍ１の重心までの距
離をＬ１とし、連接棒６を含めたピストン２ａ，２ｂの
重量をＡとすると、Ａ×Ｒ１＝Ｍ１×Ｌ１となるように
Ｍ１，Ｌ１が設定されている。ここでＲ１は遊星歯車１
０の半径である。また、釣合錘Ｍ２はクランク部材１４
の軸部１４ａを中心とする静的および動的重量バランス
（すなわち遊星歯車１０の公転重量バランス）をとるた
めのものであって、クランク部材１４の軸部１４ａから
釣合錘Ｍ２の重心までの距離をＬ２とし、前記重量Ａに
遊星歯車１０とクランク部材１４の腕部１４ｂの重量を
加算した重量をＢとすると、Ｂ×Ｒ２＝Ｍ２×Ｌ２とな
るようにＭ２，Ｌ２が設定されている。ここでＲ２はク
ランク部材１４の軸部１４ａの中心Ｏからクランク部材
１４の腕部１４ｂの先端までの長さである。Explaining the counterweights M1 and M2, first, M1 is for balancing the static and dynamic weights around the shaft hole 30 of the planetary gear 10 (that is, the rotation weight balance of the planetary gear 10). As shown in FIG. 3, assuming that the distance from the center of the planetary gear 10 to the center of gravity of the counterweight M1 is L1 and the weight of the pistons 2a and 2b including the connecting rod 6 is A, A × R1 = M1 M1 and L1 are set so as to be × L1. Where R1 is the planetary gear 1
It has a radius of 0. Further, the counterweight M2 is the crank member 14
For balancing the static and dynamic weights centering on the shaft portion 14a (that is, the revolution weight balance of the planetary gear 10) from the shaft portion 14a of the crank member 14 to the center of gravity of the counterweight M2. If the distance is L2 and the weight A is the weight of the planetary gear 10 and the weight of the arm portion 14b of the crank member 14 is B, then M2 and L2 are set so that B × R2 = M2 × L2. . Here, R2 is the length from the center O of the shaft portion 14a of the crank member 14 to the tip of the arm portion 14b of the crank member 14.
【００１８】前述の釣合式で釣合錘Ｍ１を軽量化するに
は、屈曲軸部２０の材料をできるだけ遊星歯車１０の自
転中心から離間した位置に偏在させるか、距離Ｌ１を延
長する。同様に釣合錘Ｍ２を軽量化するには、クランク
部材１４の材料をできるだけ遊星歯車１０の公転中心か
ら離間した位置に偏在させるか、距離Ｌ２を延長する。
ただし、距離Ｌ１，Ｌ２の延長は組立体１の外形寸法に
も影響してくるので、組立体１をコンパクトにするため
にはこれら寸法を適当な大きさに抑える必要がある。In order to reduce the weight of the counterweight M1 by the above-described balance method, the material of the bending shaft portion 20 is unevenly distributed at a position as far as possible from the rotation center of the planetary gear 10, or the distance L1 is extended. Similarly, in order to reduce the weight of the counterweight M2, the material of the crank member 14 is unevenly distributed as far as possible from the revolution center of the planetary gear 10, or the distance L2 is extended.
However, since the extension of the distances L1 and L2 also affects the outer dimensions of the assembly 1, these dimensions must be suppressed to appropriate sizes in order to make the assembly 1 compact.
【００１９】ハウジング１８の両端はクランク部材の両
端面を隙間をあけて覆うように端壁部１８ｂで閉塞さ
れ、この端壁部１８ｂに油供給口３４が形成されてい
る。この油供給口３４はクランク部材１４の油孔３６，
３８と連通され、一方の油孔３６、軸孔３０および屈曲
軸部２０の油孔３７を経由して連接棒６の支持部である
軸部１２外周面の潤滑がなされ、他方の油孔３８および
隙間３２をそれぞれ経由してクランク部材１４を支持す
る軸受２６および２８の潤滑がなされるようになってい
る。Both ends of the housing 18 are closed by end wall portions 18b so as to cover both end surfaces of the crank member with a gap, and oil supply ports 34 are formed in the end wall portions 18b. The oil supply port 34 has an oil hole 36 in the crank member 14,
38, the outer peripheral surface of the shaft portion 12, which is the support portion of the connecting rod 6, is lubricated through the oil hole 36, the shaft hole 30, and the oil hole 37 of the bending shaft portion 20, and the other oil hole 38. The bearings 26 and 28 for supporting the crank member 14 are lubricated via the clearance 32 and the clearance 32, respectively.
【００２０】以上、内燃機関−コンプレッサ組立体１を
例に本発明の実施形態を説明したが、本発明はコンプレ
ッサに代えて直線往復移動する移動体を有する被駆動機
械であればすべて適用でき、例えば振動式地面打固め装
置などにも適用できる。Although the embodiment of the present invention has been described above by taking the internal combustion engine-compressor assembly 1 as an example, the present invention can be applied to any driven machine having a moving body that moves linearly in reciprocation instead of the compressor. For example, it can be applied to a vibration type ground compaction device.
【００２１】[0021]
【発明の効果】本発明は前述の如く、内燃機関のピスト
ンの直線往復動を連接棒を介してそのまま被駆動機械の
移動体に伝達して移動体を直線往復動させるようにした
ので、従来のクランク装置を利用した動力伝達機構のよ
うにピストンスラップ等に起因する効率上のロスや振
動、騒音がなく、きわめて効率的かつ静粛な動力伝達が
実現できる。また内燃機関と被駆動機械を直線的に配設
するので、組立体を縦置きにすれば設置スペースが非常
に少なくて済む。As described above, according to the present invention, the linear reciprocating motion of the piston of the internal combustion engine is directly transmitted to the moving body of the driven machine through the connecting rod to linearly reciprocate the moving body. Unlike the power transmission mechanism using the crank device, there is no efficiency loss, vibration, or noise due to the piston slap and the like, and extremely efficient and quiet power transmission can be realized. Further, since the internal combustion engine and the driven machine are arranged linearly, if the assembly is installed vertically, the installation space is very small.
【００２２】また、遊星歯車の中心部回りの静的および
動的重量バランスと、クランク部材の軸部回りの静的お
よび動的重量バランスをとることにより、振動を防止し
動力伝達効率をよりよくすることができる。Further, by balancing the static and dynamic weight around the center of the planetary gear and the static and dynamic weight around the shaft of the crank member, vibration is prevented and power transmission efficiency is improved. can do.
【００２３】また、内周太陽歯車の内側空間であって、
遊星歯車を除く空間にクランク部材の腕部を回転自在に
収容することにより、本発明組立体をコンパクトに構成
することができる。In the inner space of the inner sun gear,
The assembly of the present invention can be made compact by rotatably accommodating the arms of the crank member in a space other than the planetary gears.
【図１】内燃機関−コンプレッサ組立体の概略縦断面
図。FIG. 1 is a schematic vertical sectional view of an internal combustion engine-compressor assembly.
【図２】内燃機関−コンプレッサ組立体の具体的な縦断
面図。FIG. 2 is a detailed vertical sectional view of an internal combustion engine-compressor assembly.
【図３】内燃機関−コンプレッサ組立体の重量バランス
を説明する構成図。FIG. 3 is a configuration diagram illustrating a weight balance of an internal combustion engine-compressor assembly.
【図４】（ａ）（ｂ）（ｃ）は、内燃機関とコンプレッ
サの動力伝達構造の３つの種類を示す概略図。4A, 4B and 4C are schematic views showing three types of power transmission structures of an internal combustion engine and a compressor.
１…内燃機関−コンプレッサ組立体 ２ａ…内燃機関のピストン ２ｂ…コンプレッサのピストン（移動体） ６…連接棒 ８ａ…内周太陽歯車 １０…遊星歯車 １４…クランク部材 Ｅ…内燃機関 Ｃ…コンプレッサ DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine-compressor assembly 2a ... Piston of internal combustion engine 2b ... Piston (moving body) of compressor 6 ... Connecting rod 8a ... Inner sun gear 10 ... Planetary gear 14 ... Crank member E ... Internal combustion engine C ... Compressor
Claims (3)
直線往復移動可能なピストンを有する内燃機関及び直線
往復移動可能な移動体を有する被駆動機械と、 前記内燃機関と被駆動機械の中間位置の前記一直線上に
中心Ｏを有し固定的に配設された内周太陽歯車と、 前記内周太陽歯車と噛合して自転及び公転可能であっ
て、前記内周太陽歯車のピッチ円直径の二分の一のピッ
チ円直径を有する遊星歯車と、 前記遊星歯車の中心部を自転可能に支持する腕部と、前
記遊星歯車の公転を許容するように前記中心Ｏの回りに
回転自在な軸部とを有するクランク部材と、 前記内燃機関のピストンと前記被駆動機械の移動体との
間で前記一直線に沿って延在し、前記ピストンと移動体
を前記遊星歯車の外周部分に枢支連結する連接棒とを有
することを特徴とする内燃機関と被駆動機械の直結型組
立体。1. Arranged in alignment with each other,
An internal combustion engine having a linearly reciprocating piston and a driven machine having a linearly reciprocating movable body, and a fixed arrangement having a center O on the straight line at an intermediate position between the internal combustion engine and the driven machine. An inner sun gear, a planetary gear that meshes with the inner sun gear and can rotate and revolve, and has a pitch circle diameter that is ½ of the pitch circle diameter of the inner sun gear; A crank member having an arm portion that rotatably supports the center portion of the gear, and a shaft portion that is rotatable around the center O so as to allow the revolution of the planetary gear, a piston of the internal combustion engine, and the covered member. An internal combustion engine characterized by having the piston and a connecting rod that extends along the straight line with a moving body of a drive machine and pivotally connects the piston and the moving body to an outer peripheral portion of the planetary gear and a driven body. Direct machine type assembly.
的重量バランスがとられ、かつ、前記クランク部材の軸
部回りの静的および動的重量バランスがとられているこ
とを特徴とする請求項１記載の内燃機関と被駆動機械の
直結型組立体。2. A static and dynamic weight balance around the central portion of the planetary gear and a static and dynamic weight balance around the shaft portion of the crank member. A direct coupling type assembly of an internal combustion engine and a driven machine according to claim 1.
前記遊星歯車を除く空間に前記クランク部材の腕部が回
転自在に収容されていることを特徴とする請求項１記載
の内燃機関と被駆動機械の直結型組立体。3. An inner space of the inner peripheral sun gear,
The direct coupling assembly of an internal combustion engine and a driven machine according to claim 1, wherein the arm portion of the crank member is rotatably accommodated in a space excluding the planetary gear.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28493495A JP2895431B2 (en) | 1995-11-01 | 1995-11-01 | Direct-coupled assembly of internal combustion engine and driven machinery |
| PCT/JP1996/003604 WO1998026165A1 (en) | 1995-11-01 | 1996-12-09 | Assembly for direct connection of internal combustion engine and machine driven |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28493495A JP2895431B2 (en) | 1995-11-01 | 1995-11-01 | Direct-coupled assembly of internal combustion engine and driven machinery |
| PCT/JP1996/003604 WO1998026165A1 (en) | 1995-11-01 | 1996-12-09 | Assembly for direct connection of internal combustion engine and machine driven |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09125981A true JPH09125981A (en) | 1997-05-13 |
| JP2895431B2 JP2895431B2 (en) | 1999-05-24 |
Family
ID=26437276
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28493495A Expired - Fee Related JP2895431B2 (en) | 1995-11-01 | 1995-11-01 | Direct-coupled assembly of internal combustion engine and driven machinery |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2895431B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008267468A (en) * | 2007-04-19 | 2008-11-06 | Lwj Kk | Crank device |
| JP2010193710A (en) * | 2008-06-11 | 2010-09-02 | Lwj Kk | Wire winding machine |
| WO2010150307A1 (en) * | 2009-06-23 | 2010-12-29 | Namikoshi Hiromichi | Internal combustion engine |
| CN114718720A (en) * | 2022-03-17 | 2022-07-08 | 刘平 | Multi-straight-rod piston transmission mechanism |
-
1995
- 1995-11-01 JP JP28493495A patent/JP2895431B2/en not_active Expired - Fee Related
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008267468A (en) * | 2007-04-19 | 2008-11-06 | Lwj Kk | Crank device |
| JP2010193710A (en) * | 2008-06-11 | 2010-09-02 | Lwj Kk | Wire winding machine |
| WO2010150307A1 (en) * | 2009-06-23 | 2010-12-29 | Namikoshi Hiromichi | Internal combustion engine |
| CN102149914A (en) * | 2009-06-23 | 2011-08-10 | 浪越博道 | Internal combustion engine |
| JP5089771B2 (en) * | 2009-06-23 | 2012-12-05 | 博道 浪越 | Internal combustion engine |
| CN114718720A (en) * | 2022-03-17 | 2022-07-08 | 刘平 | Multi-straight-rod piston transmission mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2895431B2 (en) | 1999-05-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| WO1998026165A1 (en) | Assembly for direct connection of internal combustion engine and machine driven | |
| US4509378A (en) | Reciprocating machines with both primary and secondary counter rotating balancers | |
| EP2257700B1 (en) | A reciprocating piston mechanism and a method of increasing internal egr in an internal combustion engine | |
| JP4959896B2 (en) | Inner cycloid engine | |
| JPS6246744B2 (en) | ||
| JP4947793B2 (en) | Crank device | |
| US6098477A (en) | Crank device for linear motion of connecting rod | |
| JP3626018B2 (en) | Directly connected reciprocating crank unit | |
| JPH09125981A (en) | Direct-coupled assembly of internal combustion engine and driven machinery | |
| US6240794B1 (en) | Crank assembly | |
| CN1082136C (en) | Assembly for direct connecting of internal combustion engine and machine driven | |
| US6148776A (en) | Bearing arrangement | |
| JP2009121540A (en) | Crank device | |
| JP3107738B2 (en) | Crank device | |
| CN111765229A (en) | Tooth-cooperated swash plate rotary cylinder type axial piston driving device | |
| US6205972B1 (en) | Engine | |
| JP3426113B2 (en) | Reciprocating piston mechanism | |
| CN2186327Y (en) | Planet sine rotary motion-rectilinear reciprocating motion change structure | |
| RU1788301C (en) | Reciprocating-piston machine | |
| WO2011044743A1 (en) | Mechanism for converting between reciprocating motion and rotary motion, components thereof and machine obtained therefrom | |
| RU2016239C1 (en) | Positive displacement engine | |
| JPH03352A (en) | Reciprocating transmission device | |
| JPH11343801A (en) | Reciprocating piston engine and linking mechanism | |
| CA1235000A (en) | Reciprocating machine with both primary and secondary counter rotating balancers | |
| RU2062326C1 (en) | Piston engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 19990126 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090305 Year of fee payment: 10 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090305 Year of fee payment: 10 |
|
| S533 | Written request for registration of change of name |
Free format text: JAPANESE INTERMEDIATE CODE: R313533 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090305 Year of fee payment: 10 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100305 Year of fee payment: 11 |
|
| LAPS | Cancellation because of no payment of annual fees |