JP2000008801A - Reciprocating machine - Google Patents
Reciprocating machineInfo
- Publication number
- JP2000008801A JP2000008801A JP22351598A JP22351598A JP2000008801A JP 2000008801 A JP2000008801 A JP 2000008801A JP 22351598 A JP22351598 A JP 22351598A JP 22351598 A JP22351598 A JP 22351598A JP 2000008801 A JP2000008801 A JP 2000008801A
- Authority
- JP
- Japan
- Prior art keywords
- connecting rod
- rotating shaft
- eccentric pin
- cylinder
- reciprocating machine
- 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- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/002—Integrally formed cylinders and cylinder heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F7/0002—Cylinder arrangements
- F02F7/0019—Cylinders and crankshaft not in one plane (deaxation)
-
- 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
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Compressor (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は内燃機関、ガス気圧縮
機、ポンプ等として用いられる往復ピストンを有する往
復運動機械に係わり、本体を小型化したものに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reciprocating machine having a reciprocating piston used as an internal combustion engine, a gas compressor, a pump or the like, and relates to a downsized main body.
【０００２】[0002]
【従来の技術】一般に内燃機関、ガス圧縮機、ポンプ等
として用いられる往復運動機械は回転軸の軸心から偏心
した位置にある偏心ピンとピストンピンとを連結する連
接棒を有し、回転軸の回転によりピストンが往復運動を
行なって所定の機能を果す様に構成されており、往復運
動機械本体の小型化を達成する為にはピストン下死点位
置におけるピストンピンと回転軸との中心間距離を短縮
する事が必要である．しかしながら一方では連接棒の大
端部がシリンダーと干渉を起す、カウンターウェイトと
ピストンとが干渉を起す等の問題を生じる為、小型化に
は限界があった。更にピストンと回転軸とが非常に接近
する様になるから（両者間に余裕がない）、回転軸に所
定の大きさを有するウェブを設け、このウェブに偏心ピ
ンを圧入する組立式は採用不可で、必然的に一体式とな
り、従って連接棒の大端部を分割型とせざるを得ず、構
造が複雑でコスト高となる欠点があった．2. Description of the Related Art A reciprocating machine generally used as an internal combustion engine, a gas compressor, a pump or the like has a connecting rod for connecting an eccentric pin located at a position eccentric from an axis of a rotating shaft and a piston pin. The reciprocating motion of the piston causes the piston to perform a predetermined function.To achieve the miniaturization of the reciprocating machine body, the center distance between the piston pin and the rotating shaft at the piston bottom dead center position is shortened. It is necessary to do. However, on the other hand, there is a problem that the large end of the connecting rod interferes with the cylinder, and the counterweight and the piston interfere with each other. Furthermore, since the piston and the rotating shaft come very close to each other (there is no room between them), an assembly type in which a web having a predetermined size is provided on the rotating shaft and an eccentric pin is pressed into this web cannot be adopted. Therefore, the connecting rod was inevitably integrated, so that the large end of the connecting rod had to be divided, resulting in a complicated structure and high cost.
【０００３】[0003]
【発明が解決しようとする問題点】本発明の目的は、ピ
ストンピン用穴のボス部外壁面と回転軸外壁面との最接
近距離を短縮する事によって往復運動機械本体を小型化
する事であり、連接棒の大端分を一体型とする事によっ
て回転軸の一端部から差し込んで偏心ピンに嵌め込む構
造とし、以って連接棒の構造を簡素化し、低コストとす
るところにある．SUMMARY OF THE INVENTION It is an object of the present invention to reduce the size of the main body of a reciprocating machine by shortening the closest distance between the outer wall surface of the boss portion of the hole for the piston pin and the outer wall surface of the rotating shaft. There is a structure in which the large end of the connecting rod is integrated so that it can be inserted from one end of the rotating shaft and fitted into the eccentric pin, thereby simplifying the structure of the connecting rod and reducing the cost.
【０００４】[0004]
【問題点を解決する為の手段】本発明は回転軸の軸心か
ら偏心した位置にある偏心ピンとピストンピンとを連結
する連接棒を備えた往復運動機械において、ピストンピ
ン用穴のボス部外壁面と回転軸外壁面との最接近距離を
シリンダー内径の０．４倍以下とし、連接棒の大端部と
の干渉を防ぐシリンダー内径の０．５倍以下の幅を有す
る切欠きをシリンダーに形成し、第１の発明では偏心ピ
ンの外周の一部が回転軸の軸受部にある外周面の軸方向
延長面よりも内部にある様に構成し、更に連接棒の大端
部を回転軸の軸方向にずらして偏心ピンから完全に抜き
事ができ、かつ連接棒の大端部の幅よりも大きい一定区
間を回転軸と偏心ピンとを連結する連結アームの所定部
に形成しており、第２の発明では偏心ピンの全周が回転
軸の軸受部にある外周面の軸方向延長面の内部にはない
様に構成してあり、第１の発明でも第２の発明でも連接
棒の大端部を回転軸の一端部から差し込んで偏心ピンに
嵌め込む構造とした．SUMMARY OF THE INVENTION The present invention relates to a reciprocating machine provided with a connecting rod for connecting an eccentric pin and a piston pin at a position eccentric from the axis of a rotary shaft. The closest distance between the shaft and the outer wall of the rotating shaft is 0.4 times or less of the cylinder inside diameter, and a notch is formed in the cylinder with a width of 0.5 times or less the cylinder inside diameter to prevent interference with the large end of the connecting rod. According to the first aspect of the present invention, a part of the outer periphery of the eccentric pin is configured to be inside the axially extending surface of the outer peripheral surface of the bearing portion of the rotating shaft, and the large end of the connecting rod is further connected to the rotating shaft. A fixed section that can be completely removed from the eccentric pin by being displaced in the axial direction and that is larger than the width of the large end of the connecting rod is formed in a predetermined portion of the connecting arm that connects the rotating shaft and the eccentric pin. In the invention of the second aspect, the entire circumference of the eccentric pin is in the bearing of the rotating shaft. In the first and second inventions, the large end of the connecting rod is inserted from one end of the rotating shaft and fitted into the eccentric pin in such a manner that it is not inside the axially extending surface of the peripheral surface. It was.
【０００５】[0005]
【実施例】図１は本発明による往復運動機械の一実施例
で、先ず図１（イ）においてピストン３の下降行程によ
り排気通路１４が開かれた後に掃気通路１２が開かれる
と、クランク室２内で予圧された混合気がシリンダー１
内へ流入し、既燃ガスを掃気する．掃気過程を経てシリ
ンダー１内に留まった新気（混合気）はピストン３の上
昇行程により圧縮を受けつつ上死点付近で点火されて燃
焼し、爆発力を発生する（２サイクル内燃機関であ
る。）一方、ピストン３の上昇行程により吸入通路１１
が開かれると気化器により生成された混合気がクランク
室２内に吸入される。本往復運動機械はＡ−Ａ′線で分
割され、各々はボルトにより締結されている．連結アー
ム９（一般にはクランクアームと呼称）は回転軸１０
（一般にはクランク軸）の軸心から偏心した位置にある
偏心ピン８（一般にはクランクピン）と回転軸１０とを
連結しており、偏心ピン８とピストンピン４とを連結す
る連接棒７が備えられ、図１（イ）では偏心ピン８の外
周の一部が回転軸１０の軸受部２０にある外周面の軸方
向延長面よりも内部にある（図１（イ）の側面図を示し
た図１（ロ）参照）。連接棒７の大端部は分割型ではな
く一体型であり、図１（ロ）の如く連接棒７の大端部を
回転軸１０の軸方向にずらして偏心ピン８から完全に抜
く事ができ、かつ連接棒７の大端部の幅よりも大きい一
定区間Ｈを連結アーム９の所定部に形成してある．従っ
て図３（イ）の如く連接棒７の大端部を回転軸１０の一
端部から差し込んで図の位置まで下げ、更に回転軸１０
の軸方向にずらせば偏心ピン８に嵌め込む事ができる．
この時、連接棒７の大端部の内径をａ′とすればｈ＜ｄ
である。１０′は軸受２０の為の肩部であり、この一部
を図３（ロ）の如く除去すれば、ｈ＜ｄの範囲内におい
て連結アーム９を太くして強度・剛性を増す事ができ
る．尚、軸受２０は滑り軸受を用いる事もできる．本発
明では図２の如くピストンピン用穴のボス部５の外壁面
と回転軸１０の外壁面との最接近距離ｌ（下死点におけ
る距離）を非常に小さくして小型化を徹底追求してい
る．即ち、一般にシリンダー内径をＤとするとピストン
スカート高さＬ＝０．４６×（１．１５＋０．０８）・
Ｄ≒０．５７×Ｄ，ピストンピン用穴のボス部５の外径
＝０．４４・Ｄとして与えられる（内燃機関，Ｖｏｌ１
６，Ｎｏ１９３，臨時増刊，ｐ７８）．従ってピストン
スカート端部と回転軸外壁面との干渉防止の為の余裕Ｓ
をＤ＝３０〜１００ｍｍクラスで２ｍｍとすると、Ｓ＝
（０．０２〜０．０６７）・Ｄであるからｌ＝Ｌ−
０．４４・Ｄ／２ ＋Ｓ≒０．４・Ｄとなる．本発明で
はピストンスカート端部と回転軸外壁面との干渉がない
範囲内での一般的限界という意味で前記ｌの値を０．４
・Ｄ以下としているところに特徴がある．図１（イ）の
本発明では小型化を極限にまで追求したもので、ピスト
ン３のスカート端部に回転軸１０がくい込んで来るのを
許す切欠き６を形成し（切欠き６により両者の干渉はな
い）、ピストンピン用穴のボス部外壁面と回転軸外壁面
との最接近距離ｌを非常に小さくして（例えば２ｍｍ）
いる．更に連接棒７の大端部との干渉を防ぐ切欠き１５
をシリンダー１に形成してあるが、Ａ−Ａ′線断面を示
す図１（ニ）の如く連接棒７の大端部の両端面は切欠き
１５内で各々１．５〜２ｍｍ位の間隙が必要であり、一
方切欠き１５の幅Ｗが最大であるとピストンスカート部
とシリンダー内壁面との接触面積が少なくなって、振動
・打音を生じさせる恐れがある．この様な事情を鑑み、
本発明では切欠き１５の幅Ｗをシリンダー内径の０．５
倍以下とした（より好ましくは０．４倍以下が良い）。
本発明では回転軸１０から偏心ピン８，連接棒７を経て
ピストン３までの部分の運動により生じる不釣り合い慣
性力を軽減する為のカウンターウェイトは前記最接近距
離ｌが非常に小さい為、クランク室２内には装着でき
ず、図１（ロ）の如くクランク室２の外部に備える様に
する（低回転で使用する場合は、カウンターウェイトを
除去しても良い）。一般には回転軸１０の両端部には冷
却用ファン１６とリコイルプーリ１８とが装着されるか
ら、カウンターウェイト１７，１９は各々に直接固定す
るか、内蔵させる構造とする．本発明では連接棒長さ
（大端部と小端部との中心間距離）と偏心ピン８の回転
半径との比が小さい為、往復慣性質量を減らして二次振
動を抑制する必要上、Ａｌ合金等の軽合金製連接棒が望
ましい。偏心ピン８にはころがり軸受を用いる事もでき
る．掃気通路についてはクランク室２の底部から軸受２
０の外側を通ってシリンダー内に開口させる事は困難を
伴なう為、図示の如く排気通路１４側から延びて来て軸
受２０の外周部近傍に到り、この曲折部１３で曲折した
後にシリンダー内へ開口する様に構成する事が望ましい
（軸受２０に針状ころ軸受を用いると、掃気通路１２の
高さに余裕ができる）。図１（ロ）において偏心ピン８
の全周が回転軸１０の軸受部にある外周面の軸方向延長
面の内部にはない様に構成したものに相当する発明を、
図１（ハ）に示す（図では偏心ピン８の外周に対して回
転軸１０の軸受部にある外周面の軸方向延長面が内接し
ている）．図からも明らかな様に図１（ロ）の連結アー
ム９を不要とする事ができる（但し、同一ピストンスト
ロークで比較すると、偏心ピン８の外径は図１（ロ）の
場合より大き目となる）．連接棒７の大端部を回転軸１
０の一端部から差し込んで偏心ピン８に嵌め込む事がで
きる為、連接棒７の大端部は分割型ではなく、一体型で
ある．図４（イ）は本発明を４サイクル内燃機関に適用
したもので、２１は吸入弁、２２は排気弁で、図示はし
ていないが回転軸１０の回転の１／２に減速して駆動さ
れるカムにより例えばプッシュロッド、ロッカーアーム
を介して駆動される（これは公知である）．図４（ロ）
は本発明をガス圧縮機、ポンプ等の流体機械に適用した
もので、吸入弁２３（ソード弁式）を介してシリンダー
内に吸入した流体（気体、液体）を圧縮した後に昇圧し
て吐出弁２４（ソード弁式）を介して吐出するものであ
る．いずれもピストンピン用穴のボス部外壁面と回転軸
外壁面との最接近距離をシリンダー内径の０．４倍以下
とし、連接棒７の大端部との干渉を防ぐシリンダー内径
の０．５倍以下（より好ましくは０．４倍以下）の幅を
有する切欠き１５をシリンダーに形成してある．偏心ピ
ン８に関しては、既に述べた様にその外周の一部が回転
軸１０の軸受部にある外周面の軸方向延長面よりも内部
にある場合と、その全周が回転軸１０の軸受部にある外
周面の軸方向延長面の内部にはない場合とがあり、いず
れも連接棒７の大端部を回転軸１０の一端部から差し込
んで偏心ピン８に嵌め込む事ができる．図４（ロ）にお
いてはクランク室２の外側にカウンターウェイトを装着
する場合は、冷却用ファンと駆動プーリとに内蔵させる
のが良い。図４（ハ）は回転軸１０の軸心をシリンダー
の軸心から偏心させたもので（模式的に示した）、スラ
スト側に偏心させる事によりピストン側面に働くスラス
トを減少させ、摩擦及び磨耗を減少させる事ができる．
本発明の様に連接棒の長さが短かい場合は、特に有効で
ある．尚、本発明では図４（ニ）の如くピストンピン用
穴のボス部５に回転軸外壁面との干渉を防ぐ切欠き２５
を形成すれば、ピストンピン用穴のボス部外壁面と回転
軸外壁面との最接近距離を更に短縮できるから、往復運
動機械本体の小型化は一段と進む．FIG. 1 shows an embodiment of a reciprocating machine according to the present invention. First, in FIG. 1 (a), when the scavenging passage 12 is opened after the exhaust passage 14 is opened by the downward stroke of the piston 3, the crank chamber is opened. Air-fuel mixture pre-pressurized in cylinder 2
It flows into the inside and scavenges burned gas. The fresh air (air-fuel mixture) remaining in the cylinder 1 through the scavenging process is ignited near top dead center while being compressed by the rising stroke of the piston 3 and burns to generate explosive power (a two-stroke internal combustion engine. ) On the other hand, the suction passage 11
Is opened, the air-fuel mixture generated by the vaporizer is sucked into the crank chamber 2. This reciprocating machine is divided along the line AA 'and each is fastened by bolts. The connecting arm 9 (generally called a crank arm) has a rotating shaft 10
An eccentric pin 8 (generally, a crankpin) located at a position eccentric from the axis of the crankshaft (generally, a crankshaft) is connected to the rotating shaft 10, and a connecting rod 7 for connecting the eccentric pin 8 to the piston pin 4 is provided. 1A, a part of the outer periphery of the eccentric pin 8 is located inside the axially extending surface of the outer peripheral surface of the bearing portion 20 of the rotating shaft 10 (a side view of FIG. 1A is shown). FIG. 1 (b)). The large end of the connecting rod 7 is not a split type but an integral type, and the large end of the connecting rod 7 can be completely removed from the eccentric pin 8 by shifting the large end of the connecting rod 7 in the axial direction of the rotating shaft 10 as shown in FIG. A predetermined section H which is formed and is larger than the width of the large end of the connecting rod 7 is formed in a predetermined portion of the connecting arm 9. Therefore, as shown in FIG. 3A, the large end of the connecting rod 7 is inserted from one end of the rotating shaft 10 and lowered to the position shown in FIG.
Can be fitted to the eccentric pin 8 by shifting in the axial direction.
At this time, if the inside diameter of the large end of the connecting rod 7 is a ', h <d
It is. Reference numeral 10 'denotes a shoulder for the bearing 20. If a part of the shoulder is removed as shown in FIG. 3B, the connecting arm 9 can be made thicker within the range of h <d to increase the strength and rigidity. . In addition, the bearing 20 can use a sliding bearing. In the present invention, as shown in FIG. 2, the closest distance l (distance at the bottom dead center) between the outer wall surface of the boss portion 5 of the piston pin hole and the outer wall surface of the rotary shaft 10 is made extremely small to pursue miniaturization. ing. That is, generally, assuming that the cylinder inner diameter is D, the piston skirt height L = 0.46 × (1.15 + 0.08) ·
D ≒ 0.57 × D, the outer diameter of the boss portion 5 of the piston pin hole = 0.44 · D (internal combustion engine, Vol1
6, No 193, extra edition, p78). Therefore, a margin S for preventing interference between the end of the piston skirt and the outer wall surface of the rotating shaft.
Is 2 mm in a class of D = 30 to 100 mm, S =
(0.02-0.067) · D, so l = L−
0.44 ・ D / 2 + S ≒ 0.4 ・ D. In the present invention, the value of l is set to 0.4 in the sense of a general limit within a range where there is no interference between the end of the piston skirt and the outer wall surface of the rotating shaft.
-There is a characteristic in that it is set to D or less. In the present invention shown in FIG. 1 (a), the miniaturization is pursued to the utmost, and a notch 6 is formed at the end of the skirt of the piston 3 to allow the rotary shaft 10 to penetrate. (There is no interference), and the closest distance 1 between the outer wall surface of the boss portion of the piston pin hole and the outer wall surface of the rotating shaft is made extremely small (for example, 2 mm).
Yes. Notch 15 for preventing interference with the large end of connecting rod 7
Is formed in the cylinder 1, and as shown in FIG. 1 (d) showing a cross section taken along the line AA ', both end surfaces of the large end of the connecting rod 7 have a gap of about 1.5 to 2 mm in the notch 15. On the other hand, if the width W of the notch 15 is the maximum, the contact area between the piston skirt portion and the inner wall surface of the cylinder is reduced, and there is a possibility that vibration and noise may occur. In light of these circumstances,
In the present invention, the width W of the notch 15 is set to 0.5
Times or less (more preferably 0.4 times or less is better).
In the present invention, the counterweight for reducing the unbalanced inertial force generated by the movement of the portion from the rotary shaft 10 to the piston 3 via the eccentric pin 8 and the connecting rod 7 has a very small closest approach distance l. 1 (b), it is provided outside the crankcase 2 (when used at low rotation, the counterweight may be removed). Generally, a cooling fan 16 and a recoil pulley 18 are mounted on both ends of the rotating shaft 10, so that the counterweights 17, 19 are directly fixed to each or built in. In the present invention, since the ratio between the connecting rod length (center distance between the large end and the small end) and the radius of rotation of the eccentric pin 8 is small, it is necessary to reduce the reciprocating inertial mass and suppress the secondary vibration. A connecting rod made of a light alloy such as an Al alloy is desirable. A rolling bearing can be used for the eccentric pin 8. For the scavenging passage, the bearing 2
Since it is difficult to open the inside of the cylinder through the outside of the bearing 0, it extends from the exhaust passage 14 side to reach the vicinity of the outer periphery of the bearing 20 as shown in the drawing, and after being bent at the bent portion 13, It is desirable that the opening be formed in the cylinder (the use of needle roller bearings as the bearings 20 allows the scavenging passage 12 to have a sufficient height). The eccentric pin 8 in FIG.
The invention corresponding to a configuration in which the entire circumference of the shaft does not exist inside the axially extending surface of the outer peripheral surface of the bearing portion of the rotating shaft 10,
As shown in FIG. 1 (c) (in the figure, the axially extending surface of the outer peripheral surface of the bearing portion of the rotating shaft 10 is inscribed in the outer periphery of the eccentric pin 8). As is clear from the figure, the connecting arm 9 of FIG. 1B can be omitted (however, when compared with the same piston stroke, the outer diameter of the eccentric pin 8 is larger than that of FIG. 1B). Become). Connect the large end of the connecting rod 7 to the rotating shaft 1
The connecting rod 7 can be inserted into the eccentric pin 8 by being inserted from one end of the connecting rod 7, so that the large end of the connecting rod 7 is not a split type but an integral type. FIG. 4A shows the present invention applied to a four-stroke internal combustion engine. Reference numeral 21 denotes an intake valve, and reference numeral 22 denotes an exhaust valve. It is driven by, for example, a push rod, a rocker arm (this is known). Fig. 4 (b)
Is an application of the present invention to a fluid machine such as a gas compressor or a pump, which compresses a fluid (gas, liquid) sucked into a cylinder through a suction valve 23 (sword valve type), and then pressurizes the fluid to discharge a valve. 24 (sword valve type). In any case, the closest distance between the outer wall surface of the boss portion of the hole for the piston pin and the outer wall surface of the rotary shaft is set to 0.4 times or less of the inner diameter of the cylinder, and 0.5 mm of the inner diameter of the cylinder to prevent interference with the large end of the connecting rod 7 A notch 15 having a width of not more than twice (more preferably not more than 0.4 times) is formed in the cylinder. Regarding the eccentric pin 8, as described above, a part of the outer periphery is located inside the axially extending surface of the outer peripheral surface of the bearing portion of the rotating shaft 10, and the entire periphery is the bearing portion of the rotating shaft 10. In some cases, the large end of the connecting rod 7 can be inserted from one end of the rotary shaft 10 and fitted into the eccentric pin 8 in some cases. In FIG. 4B, when a counterweight is mounted outside the crank chamber 2, it is preferable to incorporate the counterweight into the cooling fan and the drive pulley. FIG. 4 (c) shows the shaft center of the rotary shaft 10 eccentric from the shaft center of the cylinder (schematically shown). By eccentric to the thrust side, the thrust acting on the piston side surface is reduced, and friction and wear are reduced. Can be reduced.
This is particularly effective when the length of the connecting rod is short as in the present invention. In the present invention, as shown in FIG. 4 (d), a notch 25 for preventing the interference with the outer wall surface of the rotary shaft is formed in the boss portion 5 of the piston pin hole.
By forming, the closest distance between the outer wall surface of the boss portion of the hole for the piston pin and the outer wall surface of the rotary shaft can be further reduced, so that the size of the reciprocating machine can be further reduced.
【０００６】[0006]
【発明の効果】本発明ではピストンピン用穴のボス部外
壁面と回転軸外壁面との最接近距離ｌをシリンダー内径
の０．４倍以下とした．従来はこの様な構成とすると、
第１に連接棒７の大端部がシリンダーと干渉する、第２
に不釣り合い慣性力を軽減する為のカウンターウェイト
を備える場合はピストンと干渉する、第３に回転軸１０
に所定の大きさを有するウェブを設け、これに偏心ピン
８を圧入する組立式を採用する事ができない為（ウェブ
を設ける余裕がない）、連接棒の大端部を分割型とせざ
るを得ないといった問題を生じ、本発明の構成は不可能
と断じられた．即ち、この様な種々の問題を生じる為、
前記最接近距離ｌを一定値以上に縮小しようなどとは最
初から考えもつかなかったのである。これに対し本発明
では思い切った発想をし、第１の点に関しては連接棒７
の大端部との干渉を防ぐ切欠き１５をシリンダーに形成
する事で解決した（この場合、切欠き１５を形成しない
単純な発想で両者の干渉を防ごうとすれば、偏心ピン８
の回転半径を非常に小さくしなければならず、実用性は
ない．即ち、切欠き１５を形成してピストンストローク
を大きくする工夫が為されている）．しかも切欠き１５
の幅をシリンダー内径の０．５倍以下とした工夫がある
から、ピストンスカート部はシリンダー内壁面と広い面
積で接触し、振動・打音の発生は低い。第２の点に関し
てはカウンターウェイトを既成概念にとらわれる事なく
クランク室２の外部に備える様にした．第３の点に関し
ては回転軸１０の一端部から連接棒７の大端部を差し込
んで偏心ピン８に嵌め込む構造を採用する事によって連
接棒７の大端部を一体型で良い様にした（即ち、構造が
簡素化し、低コストとなる）。図１（イ）のものはピス
トン直径が４０ｍｍ，ピストンストロークが２４ｍｍ，
排気量３０ｃｃであるが、同一排気量の従来と比較する
とピストン直径は４ｍｍ大である一方、往復運動機械全
高は３２ｍｍ減少する。以上の様に本発明によれば大幅
な小型化が可能となる．According to the present invention, the closest distance l between the outer wall surface of the boss portion of the hole for the piston pin and the outer wall surface of the rotary shaft is set to 0.4 times or less the inner diameter of the cylinder. Conventionally, with this configuration,
First, the large end of the connecting rod 7 interferes with the cylinder,
If a counterweight for reducing the unbalanced inertia force is provided on the rotating shaft 10
Since a web having a predetermined size is provided and an eccentric pin 8 cannot be press-fitted into the web (there is no room for providing the web), the large end of the connecting rod must be divided. Therefore, the configuration of the present invention was deemed impossible. That is, to cause such various problems,
There was no idea from the beginning to try to reduce the closest approach distance 1 to a certain value or more. On the other hand, in the present invention, a drastic idea is made.
The problem was solved by forming a notch 15 in the cylinder to prevent interference with the large end of the eccentric pin 8 (in this case, if an attempt was made to prevent interference between the two with a simple idea without forming the notch 15).
The turning radius of must be very small, which is not practical. That is, the notch 15 is formed to increase the piston stroke.) And notch 15
The piston skirt portion comes into contact with the inner wall surface of the cylinder over a large area, and the occurrence of vibration and noise is low. Regarding the second point, the counterweight is provided outside the crankcase 2 without being bound by the existing concept. Regarding the third point, the large end of the connecting rod 7 is inserted into the eccentric pin 8 by inserting the large end of the connecting rod 7 from one end of the rotating shaft 10 so that the large end of the connecting rod 7 can be integrated. (That is, the structure is simplified and the cost is reduced). 1 (a) has a piston diameter of 40 mm, a piston stroke of 24 mm,
Although the displacement is 30 cc, the piston diameter is 4 mm larger than the conventional one with the same displacement, while the total height of the reciprocating machine is reduced by 32 mm. As described above, according to the present invention, it is possible to greatly reduce the size.
【図１】本発明による往復運動機械の断面図である．FIG. 1 is a sectional view of a reciprocating machine according to the present invention.
【図２】本発明を説明する為の基本となる往復運動機械
の断面図である．FIG. 2 is a cross-sectional view of a reciprocating machine as a basis for explaining the present invention.
【図３】連接棒をその大端部を偏心ピンに嵌め込む為の
説明図である．FIG. 3 is an explanatory view for fitting a large end of a connecting rod to an eccentric pin.
【図４】本発明の各種実施態様を説明する図である．FIG. 4 is a diagram illustrating various embodiments of the present invention.
１はシリンダー、２はクランク室、３はピストン、４は
ピストンピン、５はピストンピン用穴のボス部、６は切
欠き、７は連接棒、８は偏心ピン、９は連結アーム、１
０は回転軸、１１は吸入通路、１２は掃気通路、１３は
曲折部、１４は排気通路、１５は切欠き、１６は冷却用
ファン、１７・１９はカウンターウェイト、１８はリコ
イルプーリ、２０は軸受、２１は吸入弁、２２は排気
弁、２３は吸入弁、２４は吐出弁、２５は切欠き、１
０′は肩部である．1 is a cylinder, 2 is a crank chamber, 3 is a piston, 4 is a piston pin, 5 is a boss of a hole for a piston pin, 6 is a notch, 7 is a connecting rod, 8 is an eccentric pin, 9 is a connecting arm,
0 is a rotating shaft, 11 is a suction passage, 12 is a scavenging passage, 13 is a bent portion, 14 is an exhaust passage, 15 is a notch, 16 is a cooling fan, 17 and 19 are counterweights, 18 is a recoil pulley, and 20 is a recoil pulley. Bearing, 21 is a suction valve, 22 is an exhaust valve, 23 is a suction valve, 24 is a discharge valve, 25 is a notch,
0 'is the shoulder.
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ テーマコート゛(参考） Ｆ０４Ｂ 35/01 Ｆ０４Ｂ 39/00 １０７Ｃ 39/00 １０７ Ｆ１６Ｃ 3/18 Ｆ１６Ｃ 3/18 Ｆ０４Ｂ 35/00 １０１ ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 7 Identification symbol FI Theme coat ゛ (Reference) F04B 35/01 F04B 39/00 107C 39/00 107 F16C 3/18 F16C 3/18 F04B 35/00 101
Claims (7)
心ピンと前記回転軸とを連結する連結アーム、及び前記
偏心ピンとピストンピンとを連結する連接棒を備え、前
記偏心ピンの外周の一部が回転軸の軸受部にある外周面
の軸方向延長面よりも内部にある様に構成した往復運動
機械において、前記ピストンピン用穴のボス部外壁面と
回転軸外壁面との最接近距離をシリンダー内径の０．４
倍以下とし、前記連接棒の大端部との干渉を防ぐシリン
ダー内径の０．５倍以下の幅を有する切欠きをシリンダ
ーに形成し、更に前記連接棒の大端部を回転軸の軸方向
にずらして偏心ピンから完全に抜く事ができ、かつ連接
棒の大端部の幅よりも大きい一定区間を前記アームの所
定部に形成し、前記連接棒の大端部を回転軸の一端部か
ら差し込んで偏心ピンに嵌め込む構造とした事を特徴と
する往復運動機械．1. An eccentric pin provided at a position eccentric from an axis of a rotating shaft and a connecting arm for connecting the rotating shaft, and a connecting rod connecting the eccentric pin and a piston pin, a part of an outer periphery of the eccentric pin. In a reciprocating machine configured such that the inner surface is located inside the axially extending surface of the outer peripheral surface in the bearing portion of the rotating shaft, the closest approach distance between the outer wall surface of the boss portion of the hole for the piston pin and the outer wall surface of the rotating shaft is determined. 0.4 of cylinder inner diameter
A notch having a width of not more than 0.5 times the inner diameter of the cylinder to prevent interference with the large end of the connecting rod is formed in the cylinder, and the large end of the connecting rod is set in the axial direction of the rotating shaft. A predetermined section of the arm that can be completely removed from the eccentric pin by shifting the connecting rod and that is larger than the width of the large end of the connecting rod is formed at a predetermined portion of the arm, and the large end of the connecting rod is connected to one end of the rotating shaft. A reciprocating machine characterized by a structure that is inserted into the eccentric pin and inserted into the eccentric pin.
心ピンとピストンピンとを連結する連接棒を備え、前記
偏心ピンの全周が回転軸の軸受部にある外周面の軸方向
延長面の内部にはない様に構成した往復運動機械におい
て、前記ピストンピン用穴のボス部外壁面と回転軸外壁
面との最接近距離をシリンダー内径の０．４倍以下と
し、前記連接棒の大端部との干渉を防ぐシリンダー内径
の０．５倍以下の幅を有する切欠きをシリンダーに形成
し、更に前記連接棒の大端部を回転軸の一端部から差し
込んで偏心ピンに嵌め込む構造とした往復運動機械。2. A connecting rod for connecting an eccentric pin and a piston pin located at a position eccentric from the axis of the rotary shaft, wherein the entire circumference of the eccentric pin is defined by an axially extending surface of an outer peripheral surface at a bearing portion of the rotary shaft. In the reciprocating machine configured not to be inside, the closest distance between the outer wall surface of the boss portion of the hole for the piston pin and the outer wall surface of the rotating shaft is set to 0.4 times or less the inner diameter of the cylinder, A notch having a width of 0.5 times or less the inner diameter of the cylinder to prevent interference with the part, and a structure in which the large end of the connecting rod is inserted from one end of the rotating shaft and fitted into an eccentric pin. Reciprocating machine.
で来るのを許す切欠きを形成した請求項１又は２記載の
往復運動機械。3. The reciprocating machine according to claim 1, wherein a notch is formed in the piston skirt to allow the rotary shaft to enter.
トンまでの部分の運動により生じる不釣り合い慣性力を
軽減する為のカウンターウェイトをクランク室の外部に
備えた請求項１ないし３のいずれかに記載の往復運動機
械．4. The crankcase according to claim 1, wherein a counterweight is provided outside the crankcase to reduce unbalanced inertial force generated by movement of a portion from the rotating shaft to the piston via the eccentric pin and the connecting rod. Reciprocating machine described in 1.
心させた請求項１ないし４のいずれかに記載の往復運動
機械．5. The reciprocating machine according to claim 1, wherein the eccentricity of the rotating shaft is eccentric from the axis of the cylinder.
シリンダー内に供給された燃料を燃焼させて動力を発生
させる内燃機関である請求項１ないし５のいずれかに記
載の往復運動機械．6. The reciprocating machine according to claim 1, wherein the reciprocating machine is an internal combustion engine that generates power by burning fuel supplied into a cylinder by movement of a piston.
流体を圧接した後に昇圧して吐出する流体機構である請
求項１ないし５のいずれかに記載の往復運動機械．7. The reciprocating machine according to claim 1, wherein the reciprocating machine is a fluid mechanism that presses the fluid sucked into the cylinder and then pressurizes and discharges the fluid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22351598A JP2000008801A (en) | 1998-06-23 | 1998-06-23 | Reciprocating machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22351598A JP2000008801A (en) | 1998-06-23 | 1998-06-23 | Reciprocating machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2000008801A true JP2000008801A (en) | 2000-01-11 |
Family
ID=16799357
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22351598A Withdrawn JP2000008801A (en) | 1998-06-23 | 1998-06-23 | Reciprocating machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2000008801A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005069123A (en) * | 2003-08-26 | 2005-03-17 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| JP2007239508A (en) * | 2006-03-06 | 2007-09-20 | Nissan Motor Co Ltd | Reciprocating engine |
-
1998
- 1998-06-23 JP JP22351598A patent/JP2000008801A/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2005069123A (en) * | 2003-08-26 | 2005-03-17 | Matsushita Electric Ind Co Ltd | Hermetic compressor |
| JP2007239508A (en) * | 2006-03-06 | 2007-09-20 | Nissan Motor Co Ltd | Reciprocating engine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
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