JPS6035522B2 - Sealing device between cylinders of multi-cylinder two-stroke engine - Google Patents
Sealing device between cylinders of multi-cylinder two-stroke engineInfo
- Publication number
- JPS6035522B2 JPS6035522B2 JP5690380A JP5690380A JPS6035522B2 JP S6035522 B2 JPS6035522 B2 JP S6035522B2 JP 5690380 A JP5690380 A JP 5690380A JP 5690380 A JP5690380 A JP 5690380A JP S6035522 B2 JPS6035522 B2 JP S6035522B2
- Authority
- JP
- Japan
- Prior art keywords
- oil
- face
- cylinder
- ringed
- collar
- 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.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/06—Lubricating systems characterised by the provision therein of crankshafts or connecting rods with lubricant passageways, e.g. bores
-
- 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)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Lubrication Details And Ventilation Of Internal Combustion Engines (AREA)
- Lubrication Of Internal Combustion Engines (AREA)
Abstract
Description
【発明の詳細な説明】
本発明はクランク室圧縮式の多気筒2サイクルエンジン
におけ気筒間シール装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an inter-cylinder sealing device in a crank chamber compression type multi-cylinder two-stroke engine.
従来非接触型シール装置としては第1図のようにラビリ
ンスパッキンが広く採用されている。第1図においてラ
ビリンスパッキンーはリング状のものをカラー8の外側
に隊挿し、これを上下クランクケース2,3の軸受支持
内筒面4,5に挟み込み方式で固定し、多数の環状溝6
(ラビリンス溝)を有する内筒面を、気筒間回転軸7上
に固定したカラー8の外筒面に僅かな間隙をへだてて対
向させており、回転軸7と平行な細い油孔9と、その中
間部に蓮通した半径方向の油穴10を備え、油穴1川ま
クランクケース2内の油路11をへてオイルポンプの吐
出口へ接続している。12は1対の主軸受、13は軸受
支持内筒面4,5に固定したオイルスリンガ−、14は
クランクアーム、15はクランクピン、16,17は運
通した油路、18はオイルレシーバー、19はコンロッ
ド大端部、20は大端軸受である。Conventionally, a labyrinth packing as shown in FIG. 1 has been widely used as a non-contact sealing device. In FIG. 1, the labyrinth packing is a ring-shaped one inserted on the outside of the collar 8, which is fixed to the bearing support inner cylindrical surfaces 4, 5 of the upper and lower crankcases 2, 3 by a sandwiching method, and has a large number of annular grooves 6.
The inner cylindrical surface having a labyrinth groove is opposed to the outer cylindrical surface of a collar 8 fixed on the inter-cylinder rotation shaft 7 with a slight gap therebetween, and a thin oil hole 9 parallel to the rotation shaft 7 is formed. A radial oil hole 10 is provided in the middle thereof, and the oil hole 10 is connected to the discharge port of the oil pump through an oil passage 11 in the crankcase 2. 12 is a pair of main bearings, 13 is an oil slinger fixed to the bearing support inner cylindrical surfaces 4 and 5, 14 is a crank arm, 15 is a crank pin, 16 and 17 are oil passages, 18 is an oil receiver, 19 is a connecting rod big end, and 20 is a big end bearing.
ところが第1図の如く、環状溝6とカラー8から成るシ
ール部分(ラビリンスパツキン部分)とオイル通路にな
る油孔9を分けると、{1} ラビリンス効果をもたせ
るためには回転軸(カラー8)と固定シール部材(ラビ
リンスパッキン1)との間の寸法を、例えば0.1側程
度と極めて4・さく保つ必要があり、厳密な加工精度が
要求される。However, as shown in Fig. 1, if the seal part (labyrinth packing part) consisting of the annular groove 6 and collar 8 is separated from the oil hole 9 which becomes the oil passage, {1} In order to have a labyrinth effect, the rotating shaft (collar 8) must be separated. It is necessary to keep the dimension between the fixed sealing member (labyrinth packing 1) and the fixed sealing member (labyrinth packing 1) extremely small, for example, on the 0.1 side, and strict processing accuracy is required.
さらに髄万向長さについてもある程度の長さが必要とさ
れ、気筒間寸法が制限される。■ 仮に充分小さな間隙
及び大きな長さにしても完全なシールは不可能で、これ
による出力性能の低下は避けられない。Furthermore, the length of the marrow in all directions requires a certain amount of length, which limits the dimension between the cylinders. ■ Even if the gap is sufficiently small and the length is sufficiently large, a complete seal is impossible, and a decrease in output performance due to this is unavoidable.
【3} 回転軸と固定部材の接触を避けるべく軸振れを
吸収できる程度に間隙を拡げる必要があるが、そのよう
にするとラビリンス効果が犠牲にされる。[3} In order to avoid contact between the rotating shaft and the fixed member, it is necessary to widen the gap to an extent that can absorb shaft vibration, but doing so will sacrifice the labyrinth effect.
{4)ラピリンスパツキンlに油孔9を加工するのに手
間が掛かる。{4) It takes time and effort to process the oil holes 9 in the lapirin packing l.
一方オイルシール等の接触型シール装置を採用した場合
は、‘1} 気筒間回転軸部分が最も冷却されないとこ
ろであるため、耐熱性のある極めて特殊な材料が要求さ
れる。On the other hand, when a contact type sealing device such as an oil seal is adopted, an extremely special material with heat resistance is required because the rotating shaft portion between the cylinders is the part that is least cooled.
‘2} 接触部の摩耗によりシール機能が減退し、耐久
性が不足する。'2} The sealing function decreases due to wear of the contact parts, resulting in insufficient durability.
(3} メカニカルロスが避けられない・・・等の不具
合がある。(3) There are problems such as unavoidable mechanical losses.
本発明は上記不具合を解決するために、ラビリンス溝と
それに面した間隙をオイル通路とすることにより、油の
粘性抵抗や表面張力、慣性力を利用して気筒間のシール
性を確保するようにしたもので、第2図に実施例を示す
。In order to solve the above-mentioned problems, the present invention uses the labyrinth groove and the gap facing it as an oil passage to ensure sealing performance between the cylinders by utilizing the viscous resistance, surface tension, and inertia of oil. An example is shown in FIG.
第2図において第1図中の符号と同一符号は対応部分で
ある。In FIG. 2, the same symbols as those in FIG. 1 indicate corresponding parts.
第2図のラビリンスパッキン23はリング状部材で、上
下クランクケース2,3の軸受支持内筒面4,5に挟み
込み方式で固定してあり、その内筒面24には多数の環
状溝6が設けてあり、内筒面24とカラー8の外節面2
9は僅かな環状の間隙をへだてて対向しており、内筒面
24の中間に設けた環状のランド30(環状溝6,6の
間の部分)に油孔31が閉口している。32は○リング
である。The labyrinth packing 23 shown in FIG. 2 is a ring-shaped member that is fixed to the bearing support inner cylindrical surfaces 4 and 5 of the upper and lower crankcases 2 and 3 by a sandwiching method, and the inner cylindrical surface 24 has a large number of annular grooves 6. The inner cylindrical surface 24 and the outer segment surface 2 of the collar 8 are provided.
9 are opposed to each other with a slight annular gap therebetween, and an oil hole 31 is closed in an annular land 30 (a portion between the annular grooves 6, 6) provided in the middle of the inner cylindrical surface 24. 32 is a circle ring.
間隙部における油の片寄った流れを防止するため、カラ
ー8及びラビリンスパツキン23を、ランド30を境に
左右対称の型を用いた暁結品又はダィキヤスト製品とし
て、内外筒面24,29の精度を上げる方法は有効であ
る。エンジンの運転中、オイルポンプから吐出されたオ
イル(潤滑油)は、油路11、油孔31をへてランド3
0の部分から内外筒面24,29間の間隙を充満し、二
手に分れてカラー8の両側の主軸受12,12に供給さ
れる。In order to prevent uneven flow of oil in the gap, the collar 8 and the labyrinth packing 23 are made of molded products or die-cast products that are symmetrical with respect to the land 30, and the accuracy of the inner and outer cylindrical surfaces 24, 29 is improved. The method of increasing is effective. While the engine is running, oil (lubricating oil) discharged from the oil pump passes through the oil passage 11 and the oil hole 31 to the land 3.
0 fills the gap between the inner and outer cylindrical surfaces 24 and 29, and is divided into two parts and supplied to the main bearings 12 and 12 on both sides of the collar 8.
主軸受12を通過した潤滑油はオイルスリンガ−13を
へてオイルレシーバー18内に入り、遠心力を受けて油
路16へ入り、油路17をへて大機軸受20へ供給され
、潤滑済のオイルはそこからクランク室21内へ飛散し
、図示されていないシリンダーとピストン間の摺動部分
に供給される。このように本発明によると、
‘1)カラー8とラピリンスパツキン23の間の間隙が
油孔31から吐出される油で満たされるため、ラビリン
スパッキン23の左側の気筒のクランク室21と右側の
気筒のクランク室(符号なし)の間のシールが確実にな
る。The lubricating oil that has passed through the main bearing 12 passes through the oil slinger 13, enters the oil receiver 18, receives centrifugal force, enters the oil passage 16, passes through the oil passage 17, is supplied to the large machine bearing 20, and is lubricated. From there, the oil scatters into the crank chamber 21 and is supplied to a sliding portion (not shown) between the cylinder and the piston. As described above, according to the present invention, '1) Since the gap between the collar 8 and the lapillin packing 23 is filled with oil discharged from the oil hole 31, the gap between the labyrinth packing 23 and the crank chamber 21 of the cylinder on the left and the cylinder on the right The seal between the cylinder's crank chamber (not numbered) is ensured.
即ち一般に多気筒2サイクルエンジンの隣接気筒は普通
180oの位相差を有し、ラピリンスパッキン23の左
側の気筒のクランク室21がピストンの下降により圧縮
される行程(クランク室圧縮行程)においては、右側の
気筒のピストンは上昇中のためクランク室内は負圧状態
になる。従って隣接気筒のクランク室の圧力差が大きく
なる。このような場合、本発明においては、複数個の環
状溝6により形成される上記間隙の軸方向と直角な横断
面積が軸方向の各位暦で増加したり減少しているため上
記圧力差により間隙内の潤滑油が一方に流動しようとし
ても複雑な断面形状の間隙が潤滑油の流動に対し大きい
抵抗を与え、一方のクランク室21内で予圧されたガス
が上記間隙を通して他方のクランク室へ吹抜ける不具合
を確実に防止することができる。■ 油孔31から供給
される潤滑油の粘性が低い場合にも、ラビリンスパッキ
ン23の歯形状凹凸を有する内周とカラー8の間の間隙
により、前項と同じ理由により流通抵抗が増し、間隙内
の潤滑油が流れ難くなり、潤滑油が間隙を形成している
両壁面(カラー8の外筒面29やラピリンスパッキン2
3の内筒面24、環状溝6等)に付着してプラグの役割
を果し、クランク室21内の予圧ガスの吹抜けに対しシ
ール性を発揮する。即ち潤滑油の粘性が高い場合と同様
にガスの吹抜けを効果的に防止することができるのであ
る。‘3ー 内外筒面24,29間のクリアランスを従
来より大きくできるため、加工が容易になる。That is, in general, adjacent cylinders of a multi-cylinder two-stroke engine usually have a phase difference of 180 degrees, and in a stroke (crank chamber compression stroke) in which the crank chamber 21 of the cylinder on the left side of the lapillin packing 23 is compressed by the downward movement of the piston, Since the piston of the right cylinder is rising, the pressure inside the crank chamber is negative. Therefore, the pressure difference between the crank chambers of adjacent cylinders increases. In such a case, in the present invention, since the cross-sectional area perpendicular to the axial direction of the gap formed by the plurality of annular grooves 6 increases or decreases with each position in the axial direction, the pressure difference causes the gap to close. Even if the lubricating oil in the crank chamber 21 tries to flow in one direction, the gap with a complex cross-sectional shape provides a large resistance to the flow of the lubricating oil, and the gas pre-pressurized in one crank chamber 21 is blown into the other crank chamber through the gap. It is possible to reliably prevent the problem of it coming off. ■ Even when the viscosity of the lubricating oil supplied from the oil hole 31 is low, due to the gap between the tooth-shaped inner circumference of the labyrinth packing 23 and the collar 8, the flow resistance increases for the same reason as in the previous section. The lubricating oil becomes difficult to flow, and the lubricating oil becomes difficult to flow on both wall surfaces (outer cylindrical surface 29 of collar 8 and lapillin packing 2) where the lubricating oil forms a gap.
3, the inner cylindrical surface 24, annular groove 6, etc.) and plays the role of a plug, and exhibits sealing properties against blow-by of pre-pressure gas in the crank chamber 21. That is, gas blow-by can be effectively prevented as in the case where the lubricating oil has high viscosity. '3- The clearance between the inner and outer cylindrical surfaces 24 and 29 can be made larger than before, making processing easier.
‘4} 回転軸の振れを逃がすべく内外筒面24,29
間の間隙を増しても、その部分に潤滑油が充満している
ためシール性が落ちない。【5} 第1図のものに比べ
て軸方向の細孔(油孔9)を設ける必要がなくなるため
、ラビリンスパツキン23の加工が容易になる。'4} Inner and outer cylindrical surfaces 24 and 29 to relieve vibration of the rotating shaft
Even if the gap is increased, the sealing performance will not deteriorate because the area is filled with lubricating oil. [5} Compared to the one shown in FIG. 1, there is no need to provide axial fine holes (oil holes 9), so the machining of the labyrinth packing 23 becomes easier.
【6)ラビリンスパツキン23の長さの中間部分の油孔
31から潤滑油を供給する方式を採用したので、ラビリ
ンスパツキン23とカラー8の間の間隙内の油圧はラビ
リンスパッキン23の長さの中間部分(油孔31の部分
)が最も高く、両端部が最も低く、その間で滑らかに変
化する。[6] Since a method is adopted in which lubricating oil is supplied from the oil hole 31 in the middle of the length of the labyrinth packing 23, the oil pressure in the gap between the labyrinth packing 23 and the collar 8 is at the middle of the length of the labyrinth packing 23. The portion (the oil hole 31 portion) is the highest, the both ends are the lowest, and there is a smooth change in between.
従って間隙内にプラグの役割を果す潤滑油が充満してい
ることと相挨つて、左側気筒のクランク室21から右側
気筒のクランク室へ予圧ガスが吹抜けようとする場合に
も、又その逆に右側クランク室から左側クランク室へ予
圧ガスが吹抜けようとする場合にも、同程度の大きな抵
抗を与えることができ、両側気筒のクランク室に対し均
等なシール効果を発揮し得る利点がある。なお本発明を
具体化する時、環状溝はカラー8の外筒面29を設けて
も良く、内外筒面24,29の双方に設けても差し支え
ない。Therefore, in addition to the fact that the gap is filled with lubricating oil that acts as a plug, when the preload gas tries to blow through from the crank chamber 21 of the left cylinder to the crank chamber of the right cylinder, or vice versa. Even when the preloaded gas tries to blow through from the right-hand crank chamber to the left-hand crank chamber, it is possible to provide a similar amount of resistance, and there is an advantage that an equal sealing effect can be exerted on the crank chambers of both cylinders. Note that when embodying the present invention, the annular groove may be provided on the outer cylindrical surface 29 of the collar 8, or may be provided on both the inner and outer cylindrical surfaces 24 and 29.
カラー8を省略してラビリンスパッキン23の厚さを増
すこともでき、又ラビリンスパツキン23に相当する部
分をクランクケース2,3に一体に設けても良い。The thickness of the labyrinth packing 23 may be increased by omitting the collar 8, or the portion corresponding to the labyrinth packing 23 may be provided integrally with the crankcases 2 and 3.
第1図は従来の非接触型シール装置の縦断面図、第2図
は本発明によるシール装置の縦断面図である。
2,3…・・・上下クランクケース(エンジン本体)、
6・・・・・・環状溝、7・・・・・・気筒間回転軸、
23・・…・ラピリンスパツキン、24・・・…内筒面
、29・・・・・・外筒面、31・・・・・・油孔。
第1図第2図FIG. 1 is a longitudinal cross-sectional view of a conventional non-contact type sealing device, and FIG. 2 is a longitudinal cross-sectional view of a sealing device according to the present invention. 2, 3... Upper and lower crankcases (engine body),
6... Annular groove, 7... Inter-cylinder rotating shaft,
23... Lapilin packing, 24... Inner cylinder surface, 29... Outer cylinder surface, 31... Oil hole. Figure 1 Figure 2
Claims (1)
外径よりも直径がわずかに大きいエンジン本体側内筒面
の一方又は双方に多数の環状溝を設け、前記回転軸外筒
面とエンジン本体側内筒面の間の筒状間隙の概略中間位
置を油圧源に接続したことを特徴とする多気筒2サイク
ルエンジンの気筒間シール装置。1. A large number of annular grooves are provided in one or both of the outer cylindrical surface of the inter-cylinder rotating shaft and the inner cylindrical surface on the side of the engine body that surrounds the outer cylindrical surface and has a diameter slightly larger than the outer diameter, An inter-cylinder sealing device for a multi-cylinder two-stroke engine, characterized in that a substantially intermediate position of a cylindrical gap between a cylindrical surface and an inner cylindrical surface on the engine main body side is connected to a hydraulic power source.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5690380A JPS6035522B2 (en) | 1980-04-28 | 1980-04-28 | Sealing device between cylinders of multi-cylinder two-stroke engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP5690380A JPS6035522B2 (en) | 1980-04-28 | 1980-04-28 | Sealing device between cylinders of multi-cylinder two-stroke engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS56154111A JPS56154111A (en) | 1981-11-28 |
JPS6035522B2 true JPS6035522B2 (en) | 1985-08-15 |
Family
ID=13040403
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP5690380A Expired JPS6035522B2 (en) | 1980-04-28 | 1980-04-28 | Sealing device between cylinders of multi-cylinder two-stroke engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6035522B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04103114A (en) * | 1990-08-23 | 1992-04-06 | Toshiba Corp | Stationary induction electric machine |
-
1980
- 1980-04-28 JP JP5690380A patent/JPS6035522B2/en not_active Expired
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04103114A (en) * | 1990-08-23 | 1992-04-06 | Toshiba Corp | Stationary induction electric machine |
Also Published As
Publication number | Publication date |
---|---|
JPS56154111A (en) | 1981-11-28 |
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