JPS6148628A - V-type internal-combustion engine - Google Patents
V-type internal-combustion engineInfo
- Publication number
- JPS6148628A JPS6148628A JP17127284A JP17127284A JPS6148628A JP S6148628 A JPS6148628 A JP S6148628A JP 17127284 A JP17127284 A JP 17127284A JP 17127284 A JP17127284 A JP 17127284A JP S6148628 A JPS6148628 A JP S6148628A
- Authority
- JP
- Japan
- Prior art keywords
- angle
- inertial force
- combustion engine
- deltabeta
- deltadelta
- 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
- F02B75/16—Engines characterised by number of cylinders, e.g. single-cylinder engines
- F02B75/18—Multi-cylinder engines
- F02B75/22—Multi-cylinder engines with cylinders in V, fan, or star arrangement
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/22—Compensation of inertia forces
- F16F15/24—Compensation of inertia forces of crankshaft systems by particular disposition of cranks, pistons, or the like
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
本発明はV形内燃機関の改良に係り、特に高次の残存不
平衡慣性力を最小値にづ−るようにしたものに関する。DETAILED DESCRIPTION OF THE INVENTION (Industrial Application Field) The present invention relates to an improvement of a V-type internal combustion engine, and particularly to one in which high-order residual unbalanced inertia force is reduced to a minimum value.
(従来技術)
従来からV形内燃機関のクランクピンに所定の偏角を設
けて1次残存不平衡慣性力をOにする所謂位相クランク
(特開昭58−113646号)が開発されている。(Prior Art) A so-called phase crank (Japanese Unexamined Patent Publication No. 113646/1982) has been developed in which the crank pin of a V-type internal combustion engine is provided with a predetermined deflection angle to reduce the primary residual unbalanced inertia force to O.
この先行技術では第6図に示すようにクランク軸のオー
バーバランス率δおよびクランクピン相対角βを
β=2α+180゜
δ−0,5
とした時に1次残存不平衡慣性力が0になるが、高次の
残存不平衡慣性力は必ずしも最小値になるとは限らない
という問題がある。In this prior art, as shown in Fig. 6, the primary residual unbalanced inertia becomes 0 when the overbalance ratio δ of the crankshaft and the relative angle β of the crank pin are set as β=2α+180°δ−0,5. There is a problem in that the higher-order residual unbalanced inertial force does not necessarily reach the minimum value.
(発明の目的)
本発明は高次の残存不平衡慣性力をも含んで残存不平衡
慣性力を最小値に近ずけることがぐきるV形内燃I!閏
を提供することを目的としている。(Objective of the Invention) The present invention is a V-type internal combustion engine that includes high-order residual unbalanced inertia force and can bring the residual unbalanced inertia force close to a minimum value. The purpose is to provide a leap.
(発明の構成)
本発明は、一方のシリンダ列と他方のシリンダ列との挟
み角が60度未満のV形内燃機関において、1次不平衡
慣性力のみがOの場合に対するクランク軸のオ・−バー
バランス率の偏差分を△δ、クランクビン相対角の偏差
分をΔβ、前記挟み角をαとしたときに
β−2α+1806+Δβ
δ−0,5+△δ
(△β〉0、Δδ〉0)
と表示されるオーバーバランス率δおよびクランクビン
相対角βを、Δδおよび△βを調整することによって残
存不平衡慣性力が最小値に近ずくように設定したことを
特徴とするV形内燃機関である。(Structure of the Invention) The present invention provides a crankshaft adjustment for when only the primary unbalanced inertia force is O in a V-type internal combustion engine in which the included angle between one cylinder row and the other cylinder row is less than 60 degrees. - When the deviation of the bar balance ratio is △δ, the deviation of the crankshaft relative angle is Δβ, and the included angle is α, then β-2α+1806+Δβ δ-0,5+△δ (△β〉0, Δδ〉0) A V-type internal combustion engine characterized in that the overbalance ratio δ and the crankbin relative angle β, which are expressed as be.
(実施例)
本発明を適用した場合を示す第1図において、2を前シ
リンダとし、4を後シリンダとする。rはクランクアー
ム長さ、Lはコンロッド長さを夫1 々示
している。(Example) In FIG. 1 showing a case where the present invention is applied, 2 is a front cylinder, and 4 is a rear cylinder. r indicates the crank arm length, and L indicates the connecting rod length.
オーバーバランス率δはピストン、ピストンピン等の往
復系質量をm1カウンタパランサ6、ンランクビン8等
の回転系質量7nとしたときβ−且
で表示される。なお回転系質量nはクランク軸中心o2
挾んで対向した位置にあル遠心力が互いに打消す方向に
作用するカウンタパランサ6、多ランクビン8の質量を
相殺したものになる。The overbalance rate δ is expressed as β-and when the mass of the reciprocating system such as the piston and piston pin is defined as the mass 7n of the rotating system such as the m1 counter palancer 6 and the unranked bin 8. Note that the mass of the rotating system n is the center of the crankshaft o2
The masses of the counter-parancer 6 and the multi-rank bin 8, which are placed in opposing positions and whose centrifugal forces act in directions that cancel each other out, are canceled out.
1次不平衝慣性力の−みが0となる場合に対する、高次
のものを含んで残存不平衝慣性力が最小値となる場合の
オーバーバランス率の偏差分音△δとするとオーバーバ
ランス率δは
δ−0,5+△δ ・・・・・・(1)となる。The deviation of the overbalance rate when the residual unimpinged inertial force, including higher-order ones, is the minimum value compared to the case where the − of the first-order unimpinged inertial force is 0. If the overbalance rate is Δδ, then the overbalance rate δ is δ−0,5+Δδ (1).
同様に前シリンダ2と後シリンダ4との相対角βは偏差
分音Δβ、シリンダ挾み角faとすると、β=2α+1
80°十△β・・・・・・(2)となる。Similarly, the relative angle β between the front cylinder 2 and the rear cylinder 4 is the deviation pitch Δβ, and the cylinder angle fa is β=2α+1
80°10Δβ...(2).
第1図においてクランク回転角θの時の合成不平衝慣性
力Fは、X軸方向の不平衝慣性力成分をB’x、y軸方
向の不平衝慣性力成分をFyとするとF=訴−77Σ戸
・・・・・・(3)で表示される。このときFx
、Fyは往復系質量をm1クランクアーム長さをr1ク
ランク軸軸角度をωとすると
Fx= (”’+ Fr2) aoSa−b”mrJ
(c6’s o′+c os f−θ))−(4)E’
7= (Frl −Fr2 ) S’1na−δwr
ω2(sinθ−8fLn(β−の)−(5)で表示さ
れる。(4)式、(5)式中のFr1、Fr2はコンロ
ッド長さをL1シリンダオフセット量をεとすると
・・−・・・(6)
?r2=mrct+2(cos (0+4−β)+(λ
c、oe2(θ十予−β)−1−sin(θ十トβ)・
(λ5in(θ十μmβ)−H)”−ξ5j−n(θ十
う−β)/(1−(λ51n(qJ+ξ)2)”)・・
・・・・(7)
ただし λ=−1ξ=L
L L
となる。In Fig. 1, the resultant unimpinged inertial force F when the crank rotation angle is θ is given by B'x, the unimpinged inertial force component in the X-axis direction, and Fy, the unimpeded inertial force component in the y-axis direction. 77Σdoor...Displayed as (3). At this time, Fx
, Fy is the mass of the reciprocating system m1 The crank arm length is r1 The crankshaft axis angle is ω, then Fx = ("'+ Fr2) aoSa-b"mrJ
(c6's o'+cos f-θ))-(4)E'
7= (Frl −Fr2) S′1na−δwr
It is expressed as ω2 (sin θ - 8fLn (β -) - (5). Fr1 and Fr2 in equations (4) and (5) are the connecting rod length and L1 cylinder offset amount is ε... ...(6) ?r2=mrct+2(cos (0+4-β)+(λ
c, oe2(θjuyo-β)-1-sin(θjutoβ)・
(λ5in(θ10μmβ)-H)"-ξ5j-n(θ10-β)/(1-(λ51n(qJ+ξ)2)")...
...(7) However, λ=-1ξ=LL L.
このと@r=86M111%L7124ffl、 e
=0として計算により合成慣性力Fの最大値が最小とな
る前記偏差分Δβ、△δの挟み角αに対する特性を求め
ると第2図に示すグラフを得る。したがって任意の挾み
角aに対して最適な△β、Δδを選択して残存不平衝慣
性力Fi算出すると、αく606の範囲で1次不平衝慣
性力のみが0となる場合の残存不平衝慣性力’t100
%とした時に、△βおよび△δの最適値を選択すること
によシ残存不平衝慣性力Fが減少していることが分かる
。With this @r=86M111%L7124ffl, e
When the characteristics of the deviations Δβ and Δδ with respect to the included angle α are determined by calculating the maximum value of the resultant inertial force F to be the minimum, the graph shown in FIG. 2 is obtained. Therefore, if the residual unimpingement inertia force Fi is calculated by selecting the optimal △β, Δδ for a given angle a, then the residual unimpingement inertia force Fi becomes 0 within the range of 606 α. Impact inertia 't100
%, it can be seen that the residual unimpingement inertia force F is reduced by selecting the optimal values of Δβ and Δδ.
次にa=45°、r= 3 f) n、 L = 12
4ff。Then a = 45°, r = 3 f) n, L = 12
4ff.
ε=0とした時にクランクビン相対角βを変化させて計
算によシ得たオーバーバランス率δと係数に=F/mr
ω2の関係を第8図に示す。第8図および第2図から挾
み角αが45°の場合、δ=0.58、β=280°と
した時に係数Kが最小となることが分る。When ε=0, the overbalance rate δ obtained by calculation by changing the relative angle β of the crankshaft and the coefficient = F/mr
The relationship of ω2 is shown in FIG. It can be seen from FIG. 8 and FIG. 2 that when the angle α is 45°, the coefficient K becomes the minimum when δ=0.58 and β=280°.
(発明の効果)
以上説明したように不発8AKよれば、1次不平衝慣性
力のみがOとなる場合に対するクランク軸のオーバーバ
ランス率δの偏差分を△δ、クランクビン相対角βの偏
差分音Δβとして、高次の残存不平衝慣性力Fの最大値
が最小となるように△δ、Δβを選択したので、残存不
平衝慣性力Fを減少させることができる。しかも■形エ
ンジンの構造を変更することを要せず、偏差分△δ、Δ
βの選択のみで残存不平衝慣性力Fが減少するので、極
めて実施が容易である。(Effect of the invention) As explained above, according to the unexploded 8AK, the deviation of the overbalance rate δ of the crankshaft is △δ, and the deviation of the crankshaft relative angle β is As the sound Δβ, Δδ and Δβ are selected so that the maximum value of the high-order residual unimpulsive inertial force F is minimized, so that the residual unimpulsive inertial force F can be reduced. Moreover, it is not necessary to change the structure of the ■-type engine, and the deviations △δ, Δ
Since the residual unimpingement inertia force F is reduced only by selecting β, it is extremely easy to implement.
(別の実施例)
(1)第4図に示すように前シリンダ2、後シリンダ4
を外方にオフセットxεだけオフセット配置した場合に
は、第5図に示すようにオフセット量ε−〇の第1図の
場合よフ更に残存不平衝慣性カニpの最大値の最小値を
小さくすることができる。(Another embodiment) (1) As shown in Fig. 4, the front cylinder 2 and the rear cylinder 4
If it is offset outward by an offset xε, as shown in Figure 5, the minimum value of the maximum value of the residual unbalanced inertia crab p is further reduced compared to the case of Figure 1 with the offset amount ε-〇. be able to.
(2) 本発明は−1のシリンダ列と他方のシリンダ
列の気筒数が等しい偶数気筒■形エンジンに限らず、両
シリンダ列の往復系質量および回転系質量か互いに等し
ければ、例えば前シリンダ列が2気筒、後シリンダ列が
1気筒の奇数気筒V形エンジンにも適用できる。(2) The present invention is not limited to an even-numbered ■-type engine in which the number of cylinders in the -1 cylinder row and the other cylinder row are equal, but if the reciprocating system mass and rotating system mass of both cylinder rows are equal to each other, for example, the front cylinder row It can also be applied to an odd-numbered V-type engine with two cylinders and one cylinder in the rear cylinder row.
第1図は本発明を適用したV形2気筒エンジンの構造略
図、第2図は第1図のエンジンにおけるシリンダ挾み角
−残存不平衝慣性力、オーバーバランス率の偏差分、ク
ランクビン相対角の偏差分特性を示すグラフ、第8図は
オーツクーバランス率−係数の特性を示すグラフ、第4
図は本発明の別の実施例を示す構造略図、第5図は第4
図の場合のオフセット量−残存不平衝慣性力Fの最大値
の最小値、オーツ(−)5ランス率、クランクビン相対
角特性會示すグラフ、第6図は従来例會示す構造略図で
ある。2・・・前シリンダ、4・・・後シリンダ、6・
・・カウンタノくランサ、8・・・クランクビンFig. 1 is a structural schematic diagram of a V-type two-cylinder engine to which the present invention is applied, and Fig. 2 is a diagram showing the cylinder angle of the engine shown in Fig. 1 - residual unimpeded inertia force, deviation of overbalance ratio, and relative crankshaft angle. Figure 8 is a graph showing the characteristics of the deviation component of
The figure is a structural diagram showing another embodiment of the present invention, and FIG.
6 is a graph showing the offset amount-minimum value of the maximum value of the residual unimpingement inertia force F, the oat (-)5 lance ratio, and the relative angle characteristics of the crank bin in the case shown in FIG. 6. FIG. 6 is a schematic structural diagram showing the conventional example. 2...front cylinder, 4...rear cylinder, 6...
・・Counter Noku Ransa, 8・・Crankbin
Claims (1)
度未満のV形内燃機関において、1次不平衡慣性力のみ
が0の場合に対するクランク軸のオーバーバランス率の
偏差分を△δ、クランクピン相対角の偏差分をΔβ、前
記挟み角をαとしたときに β=2α+180°+△β δ=0.5+△δ (△β>0、Δδ>0) と表示されるオーバーバランス率δおよびクランクピン
相対角βを、△δおよびΔβを調整することによつて残
存不平衡慣性力が最小値に近ずくように設定したことを
特徴とするV形内燃機関。[Claims] The included angle between one cylinder row and the other cylinder row is 60
In a V-type internal combustion engine with a diameter of less than Adjust △δ and Δβ to overbalance rate δ and crank pin relative angle β, which are displayed as β=2α+180°+△β δ=0.5+△δ (△β>0, Δδ>0) A V-type internal combustion engine characterized in that the residual unbalanced inertia force is set so as to approach a minimum value.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP17127284A JPS6148628A (en) | 1984-08-16 | 1984-08-16 | V-type internal-combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP17127284A JPS6148628A (en) | 1984-08-16 | 1984-08-16 | V-type internal-combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS6148628A true JPS6148628A (en) | 1986-03-10 |
JPH0253651B2 JPH0253651B2 (en) | 1990-11-19 |
Family
ID=15920246
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP17127284A Granted JPS6148628A (en) | 1984-08-16 | 1984-08-16 | V-type internal-combustion engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6148628A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002055853A1 (en) * | 2001-01-10 | 2002-07-18 | Honda Giken Kogyo Kabushiki Kaisha | Odd-cylinder v-type internal combustion entine |
JP2007120429A (en) * | 2005-10-28 | 2007-05-17 | Toyota Central Res & Dev Lab Inc | Internal combustion engine and compressor |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58113646A (en) * | 1981-12-26 | 1983-07-06 | Honda Motor Co Ltd | Motorcycle |
-
1984
- 1984-08-16 JP JP17127284A patent/JPS6148628A/en active Granted
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58113646A (en) * | 1981-12-26 | 1983-07-06 | Honda Motor Co Ltd | Motorcycle |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002055853A1 (en) * | 2001-01-10 | 2002-07-18 | Honda Giken Kogyo Kabushiki Kaisha | Odd-cylinder v-type internal combustion entine |
US6745730B2 (en) | 2001-01-10 | 2004-06-08 | Honda Giken Kogyo Kabushiki Kaisha | Odd-cylinder v-type internal combustion engine |
JP2007120429A (en) * | 2005-10-28 | 2007-05-17 | Toyota Central Res & Dev Lab Inc | Internal combustion engine and compressor |
Also Published As
Publication number | Publication date |
---|---|
JPH0253651B2 (en) | 1990-11-19 |
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