WO2010001498A1 - Two-crank type internal-combustion engine - Google Patents
Two-crank type internal-combustion engine Download PDFInfo
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- WO2010001498A1 WO2010001498A1 PCT/JP2008/068835 JP2008068835W WO2010001498A1 WO 2010001498 A1 WO2010001498 A1 WO 2010001498A1 JP 2008068835 W JP2008068835 W JP 2008068835W WO 2010001498 A1 WO2010001498 A1 WO 2010001498A1
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- piston
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- combustion engine
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Classifications
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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
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
- F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
- F02B33/22—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with pumping cylinder situated at side of working cylinder, e.g. the cylinders being parallel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D15/00—Varying compression ratio
- F02D15/04—Varying compression ratio by alteration of volume of compression space without changing piston stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
- F02D17/02—Cutting-out
- F02D17/023—Cutting-out the inactive cylinders acting as compressor other than for pumping air into the exhaust system
Definitions
- the present invention relates to an internal combustion engine with improved torque and power.
- the problem to be solved is that at the angle where the moment arm of the crank is the largest, the geometrical compression ratio in the cylinder is more than doubled and the rotational torque and output of the engine are improved compared to the conventional engine. It is.
- the present invention adds an auxiliary cylinder in addition to the main cylinder conventionally contained in an engine and communicates the respective combustion chambers, and the moment arm of the main crank for the main cylinder is at the largest angle, and the auxiliary cylinder is substantially
- the rotational torque of the crank is improved by controlling the phases of each other so as to be positioned at the top dead center and suppressing the pressure drop in the communicated cylinders.
- the torque of the engine can be greatly improved by simply combining the auxiliary cylinder and the crank.
- the displacement of the engine can be reduced, and the fuel consumption and the weight of the engine can be reduced.
- the present invention is an internal combustion engine that explodes and burns vaporized fuel in a cylinder to move a piston, and rotates a crankshaft via a link connected to the piston, wherein an auxiliary piston and a rotation less than half of the piston are rotated. It consists of an auxiliary crank whose speed is twice that of the crank, and when the previous piston is at top dead center, each crank shaft is a gear or the like so that the auxiliary piston is between the bottom dead center and half the stroke.
- This two-stroke internal combustion engine is characterized in that it is connected via a transmission and the internal spaces of the cylinder heads are communicated with each other.
- the small pistons 41 are in phase such that the large pistons 31 are at the bottom dead center or at a position elevated from within the point by half or less of the stroke when the large pistons 31 are at the top dead center.
- the compression ratio of the combined cylinder is large as shown in FIG.
- FIG. 3 shows a graph in which the large and small phases when the bore ratio is 0.3 are represented by the angle of the large crank 32.
- the minus of the phase difference indicates that the large piston 31 is at the top dead center while the small piston 41 is descending, and the plus of the phase difference is that it is ascending. It can be seen that the maximum compression ratio increases as the phase difference increases regardless of plus or minus. By setting the phase difference to 30 degrees, the maximum compression ratio can be increased from 4.5 to nearly 9 practical.
- FIG. 4 shows the relationship between the above-described phase and the torque index addition obtained by multiplying the ratio of the geometric compression ratio in the cylinder 20 and the moment radius of the crank and the turning radius of the crank. Since the influence of the auxiliary crank is influenced not only by the crank rotation radius but also by the cylinder area ratio and the rotation speed ratio of the crank even at the same pressure, the value obtained by multiplying the bore ratio by 2 is considered. At the maximum compression rate in Fig. 3 there was no difference due to the sign of the phase difference, but when it comes to torque index it is better that the phase difference is plus, ie when the large piston 31 is at top dead center, it is better for the small piston 41 to ascend I understand. This torque index corresponds to about 1.5 times that in the absence of a phase difference and about 2 times that in the conventional engine.
- FIG. 5 is a cross-sectional view showing each process of the present embodiment. The respective strokes of intake, compression, explosion and exhaust are shown in order from (a) of the left figure.
- FIG. 5 shows the case of a four-stroke gasoline engine
- the present invention is not limited to this, and can be applied to a diesel engine, a two-stroke engine, and the like.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
A two-crank type internal-combustion engine increases the geometric compression rate within a cylinder twice or more in an angle at which a moment arm of a crank becomes maximum to improve the rotation torque and output of an engine compared with conventional engines. An auxiliary piston is added to a main piston contained heretofore in the engine, and combustion chambers are made to be in communication with each other. Further, the main piston and the auxiliary piston are controlled in phase such that the auxiliary piston is positioned approximately at a top dead center in an angle at which a moment arm of a main crank for the main piston becomes maximum to constrain reduction in pressure within the combustion chambers in communication. Such an arrangement improves the rotation torque of the crank.
Description
本発明は、トルクと出力を向上した内燃機関に関する。
The present invention relates to an internal combustion engine with improved torque and power.
例えば特許文献1に示されているような、ピストンとクランクをリンクで連結したいわゆるレシプロタイプの内燃機関(エンジン)では、クランクの回転トルクを発生させるためのモーメントアームが最も大きくなる状態、すなわちピストンの位置がストロークのほぼ中央では、幾何学的なシリンダ内の圧縮率は2倍以下に低下しており、トルクが有効に発生しないだけでなく、エンジンの低効率や低出力の原因となっている。
特開2007-92693号公報
For example, in a so-called reciprocating type internal combustion engine (engine) in which a piston and a crank are connected by a link as shown in Patent Document 1, a state in which a moment arm for generating a rotational torque of the crank becomes the largest At approximately the center of the stroke, the compression ratio in the geometric cylinder is less than doubled, and not only the torque does not occur effectively, but also the low efficiency and low power of the engine There is.
JP 2007-92693 A
解決しようとする問題点は、クランクのモーメントアームが最も大きくなる角度において、シリンダ内の幾何学的圧縮率を2倍以上に高め、エンジンの回転トルクや出力を従来のエンジンンに比べて向上させることである。
The problem to be solved is that at the angle where the moment arm of the crank is the largest, the geometrical compression ratio in the cylinder is more than doubled and the rotational torque and output of the engine are improved compared to the conventional engine. It is.
本発明は、エンジンンに従来含まれる主シリンダに加えて補助のシリンダを追加するとともに、それぞれの燃焼室を連通させ、主シリンダ用の主クランクのモーメントアームが最も大きく角度において、補助シリンダが略上死点に位置するようにお互いの位相を制御し、連通させたシリンダ内の圧力低下を抑制させることにより、クランクの回転トルクを向上させる。
The present invention adds an auxiliary cylinder in addition to the main cylinder conventionally contained in an engine and communicates the respective combustion chambers, and the moment arm of the main crank for the main cylinder is at the largest angle, and the auxiliary cylinder is substantially The rotational torque of the crank is improved by controlling the phases of each other so as to be positioned at the top dead center and suppressing the pressure drop in the communicated cylinders.
本考案では補助的なシリンダとクランクを組み合わせるだけでエンジンのトルクしいては出力の大幅な向上が期待できる。
In the present invention, it is expected that the torque of the engine can be greatly improved by simply combining the auxiliary cylinder and the crank.
さらに本考案ではエンジンのトルクや出力を増加させる必要がない場合には、エンジンの排気量を小さくでき、燃費やエンジンの重量を削減できる。
Furthermore, in the present invention, when it is not necessary to increase the torque and output of the engine, the displacement of the engine can be reduced, and the fuel consumption and the weight of the engine can be reduced.
本発明はシリンダ内で気化した燃料を爆発燃焼させてピストンを移動させ、ピストンに連結されたリンクを介してクランク軸を回転させる内燃機関において、排気量が前記ピストンの半分以下の補助ピストンと回転速度が前記クランクの2倍である補助クランクからなり、前期ピストンが上死点のとき、補助ピストンが下死点からストロークの半分まで上昇した位置の間となるようお互いのクランク軸を歯車等の変速器を介して連結し、お互いのシリンダヘッドの内部空間を連通せしめたことを特徴とする2サイクル内燃機関である。
The present invention is an internal combustion engine that explodes and burns vaporized fuel in a cylinder to move a piston, and rotates a crankshaft via a link connected to the piston, wherein an auxiliary piston and a rotation less than half of the piston are rotated. It consists of an auxiliary crank whose speed is twice that of the crank, and when the previous piston is at top dead center, each crank shaft is a gear or the like so that the auxiliary piston is between the bottom dead center and half the stroke. This two-stroke internal combustion engine is characterized in that it is connected via a transmission and the internal spaces of the cylinder heads are communicated with each other.
図1に示したように大小2式のピストン31,41とクランク32,42を用意し、小さいクランク軸42の回転数を大きいクランク軸31の2倍となるようギヤ等(図示せず)で連結する。
As shown in FIG. 1, two large and small pistons 31 and 41 and cranks 32 and 42 are prepared, and the rotation speed of the small crankshaft 42 is doubled that of the large crankshaft 31 with gears or the like (not shown). Link.
このとき、小さいピストン41は大きいピストン31が上死点にあるとき下死点またはここからストロークの半分以内上昇した位置にあるように位相を合わせる。
At this time, the small pistons 41 are in phase such that the large pistons 31 are at the bottom dead center or at a position elevated from within the point by half or less of the stroke when the large pistons 31 are at the top dead center.
大きいピストン31が上死点のとき小さいピストン41を下死点とし、大小のシリンダヘッド34,44を連通させたときの総合のシリンダの圧縮率は図2に示したとおり、小さいピストン41の大きいピストン31に対するボア比によって変化し、ボア比0すなわち小さいピストン41がない従来のエンジンに比べてボア比を大きくするほど大きいピストン31のモーメントアームが最大となるクランク角270度近辺での圧縮率は上昇し、トルクの増加が期待できる。
When the large piston 31 is at the top dead center and the small piston 41 is at the bottom dead center and the large and small cylinder heads 34 and 44 are communicated, the compression ratio of the combined cylinder is large as shown in FIG. The compression ratio at a crank angle of 270 degrees at which the moment arm of the piston 31 is maximized as the bore ratio increases as the bore ratio increases, as the bore ratio changes with the bore ratio to the piston 31 and the bore ratio is larger, i.e. It can be expected to increase and increase torque.
ただし、ボア比が大きくなりすぎると最大の圧縮率が低下し、圧縮行程でシリンダ内の空気が十分温度上昇しなくなる危険がある。
However, if the bore ratio becomes too large, the maximum compression rate decreases, and there is a risk that the temperature of the air in the cylinder will not rise sufficiently in the compression stroke.
そこで、大きいピストン31が上死点のとき小さいピストン41をストロークの半分以内上昇させてみる。図3にはボア比が0.3の場合の大小の位相を大きいクランク32の角度で表したグラフを示している。位相差のマイナスは大きいピストン31が上死点のとき小さいピストン41が下降中、位相差のプラスは上昇中を示す。位相差はプラスマイナスに拘わらず大きくするほど最大の圧縮率が増加することがわかる。位相差を30度に設定することにより、最大の圧縮率は4.5から実用的な9近くまで増加できる。
Therefore, when the large piston 31 is at the top dead center, the small piston 41 is raised as much as half of the stroke. FIG. 3 shows a graph in which the large and small phases when the bore ratio is 0.3 are represented by the angle of the large crank 32. The minus of the phase difference indicates that the large piston 31 is at the top dead center while the small piston 41 is descending, and the plus of the phase difference is that it is ascending. It can be seen that the maximum compression ratio increases as the phase difference increases regardless of plus or minus. By setting the phase difference to 30 degrees, the maximum compression ratio can be increased from 4.5 to nearly 9 practical.
一方、シリンダ20内の幾何学的圧縮率とクランクのモーメントアームとクランクの回転半径の比をかけたトルク指数加と上記位相との関係を図4に示す。補助クランクの影響は同じ圧力でもクランク回転半径だけでなくシリンダ面積比やクランクの回転速度比が影響するため、ボア比に2を乗じた値を考慮している。図3の最大圧縮率では位相差の符号による差はなかったが、トルク指数になると位相差はプラス、すなわち大きいピストン31が上死点のとき、小さいピストン41が上昇中であるほうが良いことが判る。このトルク指数は位相差のない場合に比べて約1.5倍、従来のエンジンと比べると約2倍に相当する。
On the other hand, FIG. 4 shows the relationship between the above-described phase and the torque index addition obtained by multiplying the ratio of the geometric compression ratio in the cylinder 20 and the moment radius of the crank and the turning radius of the crank. Since the influence of the auxiliary crank is influenced not only by the crank rotation radius but also by the cylinder area ratio and the rotation speed ratio of the crank even at the same pressure, the value obtained by multiplying the bore ratio by 2 is considered. At the maximum compression rate in Fig. 3 there was no difference due to the sign of the phase difference, but when it comes to torque index it is better that the phase difference is plus, ie when the large piston 31 is at top dead center, it is better for the small piston 41 to ascend I understand. This torque index corresponds to about 1.5 times that in the absence of a phase difference and about 2 times that in the conventional engine.
図5は本実施例の各行程を断面図で示したものである。左図の(a)から順に吸気、圧縮、爆発、排気の各行程を示す。
FIG. 5 is a cross-sectional view showing each process of the present embodiment. The respective strokes of intake, compression, explosion and exhaust are shown in order from (a) of the left figure.
図5では4サイクルのガソリンエンジンの場合を示したが、本発明はこれに限定されず、ディーゼルエンジンや2サイクルエンジン等にも応用できる。
Although FIG. 5 shows the case of a four-stroke gasoline engine, the present invention is not limited to this, and can be applied to a diesel engine, a two-stroke engine, and the like.
10 エンジン
20 シリンダブロック
31 主ピストン
41 補助ピストン
32、42 クランク
34、44 シリンダヘッド 10Engine 20 Cylinder Block 31 Main Piston 41 Auxiliary Piston 32, 42 Crank 34, 44 Cylinder Head
20 シリンダブロック
31 主ピストン
41 補助ピストン
32、42 クランク
34、44 シリンダヘッド 10
Claims (1)
- シリンダ内で気化した燃料を爆発燃焼させてピストンを移動させ、ピストンに連結されたリンクを介してクランク軸を回転させる内燃機関において、排気量が前記ピストンの半分以下の補助ピストンと回転速度が前記クランクの2倍である補助クランクからなり、前記ピストンが上死点のとき、前記補助ピストンが下死点からストロークの半分まで上昇した位置の間となるように互いのクランク軸を歯車等の変速器を介して連結し、お互いのシリンダヘッドの内部空間を連通せしめたことを特徴とする2クランク式内燃機関。 In an internal combustion engine that explodes and burns fuel vaporized in a cylinder to move a piston and rotate a crankshaft via a link connected to the piston, the auxiliary piston having a displacement equal to or less than half of the piston and the rotational speed The cranks are gear-shifted with each other such that the auxiliary piston is between the position where the auxiliary piston is raised from the bottom dead center to a half stroke when the piston is at the top dead center. A two-crank type internal combustion engine, which is connected via a cylinder and allows the internal spaces of the cylinder heads to communicate with each other.
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JP2008-172902 | 2008-07-02 | ||
JP2008172902A JP2010013960A (en) | 2008-07-02 | 2008-07-02 | Two-crank type internal combustion engine |
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Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5032304A (en) * | 1973-07-25 | 1975-03-29 | ||
JPS5139281B2 (en) * | 1972-05-12 | 1976-10-27 | ||
JPS59200021A (en) * | 1983-04-27 | 1984-11-13 | Yanmar Diesel Engine Co Ltd | In-line internal-combustion engine |
JPH02501843A (en) * | 1987-10-16 | 1990-06-21 | バン アバルマエテ ギルバート,ルシアン,チャールス,ヘンリ,ルイス | Variable volume ratio compression ignition engine |
JPH11193724A (en) * | 1997-12-27 | 1999-07-21 | Kunio Kikuchi | Internal combustion engine |
-
2008
- 2008-07-02 JP JP2008172902A patent/JP2010013960A/en active Pending
- 2008-10-17 WO PCT/JP2008/068835 patent/WO2010001498A1/en active Application Filing
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5139281B2 (en) * | 1972-05-12 | 1976-10-27 | ||
JPS5032304A (en) * | 1973-07-25 | 1975-03-29 | ||
JPS59200021A (en) * | 1983-04-27 | 1984-11-13 | Yanmar Diesel Engine Co Ltd | In-line internal-combustion engine |
JPH02501843A (en) * | 1987-10-16 | 1990-06-21 | バン アバルマエテ ギルバート,ルシアン,チャールス,ヘンリ,ルイス | Variable volume ratio compression ignition engine |
JPH11193724A (en) * | 1997-12-27 | 1999-07-21 | Kunio Kikuchi | Internal combustion engine |
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