JPS648221B2 - - Google Patents
Info
- Publication number
- JPS648221B2 JPS648221B2 JP56083419A JP8341981A JPS648221B2 JP S648221 B2 JPS648221 B2 JP S648221B2 JP 56083419 A JP56083419 A JP 56083419A JP 8341981 A JP8341981 A JP 8341981A JP S648221 B2 JPS648221 B2 JP S648221B2
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- rotating
- flywheels
- rotation
- reverse
- 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
- 238000002485 combustion reaction Methods 0.000 claims description 7
- 238000010586 diagram Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- NJPPVKZQTLUDBO-UHFFFAOYSA-N novaluron Chemical group C1=C(Cl)C(OC(F)(F)C(OC(F)(F)F)F)=CC=C1NC(=O)NC(=O)C1=C(F)C=CC=C1F NJPPVKZQTLUDBO-UHFFFAOYSA-N 0.000 description 1
Classifications
-
- 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
- F16F15/26—Compensation of inertia forces of crankshaft systems using solid masses, other than the ordinary pistons, moving with the system, i.e. masses connected through a kinematic mechanism or gear system
- F16F15/264—Rotating balancer shafts
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
- Vibration Prevention Devices (AREA)
- Jib Cranes (AREA)
- Electrical Control Of Ignition Timing (AREA)
- Supercharger (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
- Testing Of Balance (AREA)
- Optical Communication System (AREA)
Description
【発明の詳細な説明】
この発明は、内燃機関に発生する上下および左
右の１次不平衡モーメントを同時に補償するよう
にした内燃機関の１次不平衡モーメント補償装置
に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a first-order unbalanced moment compensator for an internal combustion engine that simultaneously compensates for vertical and horizontal first-order unbalanced moments generated in the internal combustion engine.
一般に、内燃機関、たとえば、４気筒のデイー
ゼル機関には、駆動時に上下および左右の１次不
平衡モーメントが発生する。そこで従来は、機関
のシヤフトの前端および後端にカウンタウエイト
を取付けたはずみ車を装着し、はずみ車がシヤフ
トの回転に伴つて回転することにより１次不平衡
モーメントの補償を行なつている。 Generally, in an internal combustion engine, for example, a four-cylinder diesel engine, vertical and horizontal first-order unbalance moments are generated when the engine is driven. Conventionally, a flywheel with a counterweight attached to the front and rear ends of the engine shaft is mounted, and the flywheel rotates as the shaft rotates to compensate for the first unbalanced moment.
しかし、前述の場合、上下の１次不平衡モーメ
ントと左右の１次不平衡モーメントとの和が一定
の関係になるため、一方の１次不平衡モーメント
の補償を行ないその１次不平衡モーメントを減少
させると、他方の１次不平衡モーメントが増加
し、上下および左右の１次不平衡モーメントを同
時に補償することは不可能である。 However, in the above case, the sum of the vertical unbalanced moment and the left and right primary unbalanced moments is a constant relationship, so one of the primary unbalanced moments is compensated for and the first unbalanced moment is If it is decreased, the other first-order unbalance moment increases, and it is impossible to compensate for the vertical and horizontal first-order unbalance moments at the same time.
また、従来、上下の２次不平衡モーメントを補
償し、一方向すなわち上下方向の起振力を減少す
るために、チエーンバランサや電動式消振機が使
用され、たとえば、チエーンバランサや電動消振
機を、上下および左右の１次不平衡モーメントの
補償に適用させた場合、カウンタウエイトや消振
機が非常に大きなものとなり、船舶のデイーゼル
機関などに搭載することは困難である。 In addition, conventionally, chain balancers and electric vibration dampers have been used to compensate for the vertical unbalanced second-order moments and reduce the excitation force in one direction, that is, the vertical direction. When this machine is applied to compensate for vertical and horizontal first-order unbalanced moments, the counterweight and vibration suppressor become very large, making it difficult to install them in a ship's diesel engine or the like.
この発明は、前記の点に留意し、簡単な構成
で、かつ、クランクシヤフトの軸線方向に若干容
積を要しても、前記軸線に直交する方向には容積
を要さず、全体として小形であり、内燃機関に生
ずる上下および左右の１次不平衡モーメントを同
時に補償する補償装置を提供することを目的とす
る。 With the above points in mind, the present invention has a simple configuration, and although it requires some volume in the axial direction of the crankshaft, no volume is required in the direction perpendicular to the axis, and the overall size is small. An object of the present invention is to provide a compensation device that simultaneously compensates for vertical and horizontal first-order unbalanced moments that occur in an internal combustion engine.
前記目的を達成するために、この発明は、クラ
ンクシヤフトの両端にそれぞれ装着され前記シヤ
フトの回転方向に回転する正回転はずみ車と、前
記シヤフトの両端の外側に前記シヤフトの軸線上
の軸にそれぞれ設けられた１個ずつの逆回転はず
み車と、前記シヤフトの両端の前記正回転はずみ
車とそれぞれの前記逆回転はずみ車との間にそれ
ぞれ介在され前記正回転はずみ車に対し前記逆回
転はずみ車を逆回転させる傘歯車と、前記両正回
転はずみ車にそれぞれ取付けられた正回転用カウ
ンタウエイトと、前記両逆回転はずみ車にそれぞ
れ取付けられた前記正回転用カウンタウエイトと
異なる重量の逆回転用カウンタウエイトとを備え
たことを特徴とする内燃機関の１次不平衡モーメ
ント補償装置である。 In order to achieve the above object, the present invention provides positive rotating flywheels that are mounted on both ends of a crankshaft and rotate in the rotational direction of the shaft, and shafts that are mounted on the outside of both ends of the shaft on the axis of the shaft. a bevel gear interposed between each of the forward rotating flywheels and each of the reverse rotating flywheels at both ends of the shaft and rotating the reverse rotating flywheel in the opposite direction with respect to the forward rotating flywheel; and a counterweight for forward rotation attached to each of the two forward rotation flywheels, and a counterweight for reverse rotation of a weight different from the counterweight for forward rotation attached to each of the two reverse rotation flywheels. This is a characteristic first-order unbalanced moment compensator for an internal combustion engine.
前記のように構成されたこの発明は、両逆回転
はずみ車が、クランクシヤフトの両端に装着され
た正回転はずみ車の外側に、前記シヤフトの軸線
上の軸に設けられ、正回転はずみ車と逆回転はず
み車が傘歯車により連結されているため、クラン
クシヤフトの回転数と同一回転数で正、逆回転は
ずみ車が回転し、上下、左右の１次不平衡モーメ
ントを同時に補償し、構成が簡単であり、かつ、
クランクシヤフトの軸線方向に若干容積を要して
も、前記軸線に直交する方向の容積を要さず、全
体として小形になる。 In the present invention configured as described above, both counter-rotating flywheels are provided on the shaft on the axis of the shaft on the outside of the normal-rotating flywheel mounted on both ends of the crankshaft, and the forward-rotating flywheel and the counter-rotating flywheel are connected by bevel gears, so the forward and reverse flywheels rotate at the same speed as the crankshaft, simultaneously compensating for vertical and horizontal first-order unbalanced moments. ,
Even if some volume is required in the axial direction of the crankshaft, no volume is required in the direction perpendicular to the axis, resulting in a small overall size.
この発明の１実施例を第１図ないし第５図を参
照して以下に説明する。 One embodiment of the invention will be described below with reference to FIGS. 1 to 5.
第１図ないし第３図において、１は４気筒のデ
イーゼル機関、２はデイーゼル機関１内に設けら
れたクランク、３はクランク２の回転により回転
するクランクシヤフト、４，５はシヤフト３の両
端に装着された２個の正回転はずみ車であり、シ
ヤフト３の回転によりシヤフト３と同方向に回転
する。６，７は両はずみ車４，５それぞれに設け
られた正回転歯車、８，９は両正回転はずみ車
４，５それぞれ外方にシヤフト３の軸線上の軸に
設けられた２個の逆回転はずみ車、１０，１１は
逆回転はずみ車８，９それぞれに設けられた逆回
転歯車、１２ａ，１２ｂは一方の正回転歯車６と
一方の逆回転歯車１１との間に設けられた２個の
一端側傘歯車であり、一方の逆回転はずみ車８を
一方の正回転はずみ車４に対し逆方向に同一の回
転数で回転させる。１３ａは一端側傘歯車１２
ａ，１２ｂの受け台、１４ａ，１４ｂは他方の正
回転歯車７と他方の逆回転歯車１０との間に設け
られた２個の他端側傘歯車であり、他方の逆回転
はずみ車９を他方の正回転はずみ車５に対し逆方
向に同一の回転数で回転させ、一端側傘歯車１２
ａ，１２ｂと同様に受け台１３ｂに取付けられて
いる。１５，１６は両回転はずみ車４，５それぞ
れに取付けられた２個の正回転用カウンタウエイ
ト、１７，１８は両逆回転はずみ車８，９それぞ
れに取付けられた２個の逆回転用カウンタウエイ
トであり、両逆回転用カウンタウエイト１７，１
８それぞれの重量が両正回転用カウンタウエイト
１５，１６それぞれの重量と異なる。なお、第３
図の矢印が回転方向を示す。 In Figures 1 to 3, 1 is a four-cylinder diesel engine, 2 is a crank installed in the diesel engine 1, 3 is a crankshaft that rotates with the rotation of the crank 2, and 4 and 5 are attached to both ends of the shaft 3. These are two forward-rotating flywheels that are mounted, and rotate in the same direction as the shaft 3 as the shaft 3 rotates. Reference numerals 6 and 7 denote positive rotation gears provided on both flywheels 4 and 5, respectively, and reference numerals 8 and 9 indicate two reverse rotation flywheels provided on shafts on the axis of the shaft 3 on the outside of both normal rotation flywheels 4 and 5, respectively. , 10 and 11 are reverse rotation gears provided on the reverse rotation flywheels 8 and 9, respectively, and 12a and 12b are two end umbrellas provided between one of the normal rotation gears 6 and one of the reverse rotation gears 11. It is a gear, and rotates one reverse-rotating flywheel 8 in the opposite direction to one forward-rotating flywheel 4 at the same rotation speed. 13a is a bevel gear 12 on one end side
The rests 14a and 14b of a and 12b are two other end bevel gears provided between the other forward rotation gear 7 and the other reverse rotation gear 10, and the other end side bevel gears are provided between the other reverse rotation flywheel 9 The bevel gear 12 on one end side is rotated in the opposite direction at the same rotation speed with respect to the forward rotating flywheel 5.
It is attached to the pedestal 13b similarly to a and 12b. Reference numerals 15 and 16 indicate two forward rotation counterweights attached to both rotating flywheels 4 and 5, respectively, and 17 and 18 indicate two counterweights for reverse rotation attached to both counterrotating flywheels 8 and 9, respectively. , counterweight for both reverse rotation 17,1
8 is different from the weight of both forward rotation counterweights 15 and 16. In addition, the third
The arrow in the figure indicates the direction of rotation.
そして、両正回転用カウンタウエイト１５，１
６の重量をＷとし、両逆回転用カウンタウエイト
１７，１８の重量をＷとし、さらにシヤフト３が
角速度ωで回転した場合、第４図に示すように、
両正回転用カウンタウエイト１５，１６それぞれ
を２個の正回転質量球１５′，１６′に置換すると
ともに、両逆回転用カウンタウエイト１７，１８
それぞれを逆回転質量球１７′，１８′に置換し、
両正回転質量球１５′，１６′それぞれのシヤフト
３の中心線からの距離をＲ１に設定するととも
に、両逆回転質量球１７′，１８′それぞれのシヤ
フト３の中心線からの距離をＲ２に設定し、さら
に、両正回転質量球１５′，１６′間の距離、およ
び両逆回転質量球１７′，１８′間の距離それぞれ
をＬ１，Ｌ２とすると、両正回転質量球１５′，
１６′および両逆回転質量球１７′，１８′それぞ
れのカツプリングモーメントma，mbが、つぎの
(1)式および(2)式それぞれで示され、ma＋mbから
求まる上下の補償用１次不平衡モーメントが生じ
るとともに、ma−mbから求まる左右の補償用１
次不平衡モーメントが生じる。 And counterweights 15,1 for both forward rotations
6 is W, the weight of both counterweights 17 and 18 is W, and the shaft 3 rotates at an angular velocity ω, as shown in FIG.
Both forward rotation counterweights 15 and 16 are replaced with two forward rotation mass balls 15' and 16', and both counterweights 17 and 18 are replaced with two forward rotation mass balls 15' and 16'.
Replace each with counter-rotating mass spheres 17' and 18',
The distance from the center line of the shaft 3 of both the normal rotating mass spheres 15' and 16' is set to R1, and the distance from the center line of the shaft 3 to each of the counter rotating mass spheres 17' and 18' is set to R2. Further, if the distance between the two normal rotating mass spheres 15', 16' and the distance between the two counter rotating mass spheres 17', 18' are respectively L1 and L2, then the two normal rotating mass spheres 15',
The coupling moments ma and mb of 16' and both counter-rotating mass spheres 17' and 18' are as follows.
As shown by equations (1) and (2), the first unbalance moment for vertical compensation determined from ma + mb is generated, and the first unbalance moment for left and right compensation determined from ma - mb is generated.
A second unbalanced moment is generated.
ma＝（Ｗ／ｇ）・Ｒ１・ω2・Ｌ１ ……(1)式
mb＝（Ｗ／ｇ）・Ｒ２・ω2・Ｌ２ ……(2)式
一方、いわゆる無補償の場合の上下および左右
の１次不平衡モーメントWva，Mhbそれぞれを
簡単な数式で表わすと、つぎの(3)式および(4)式そ
れぞれのようになる。 ma=(W/g)・R1・ω 2・L1 …(1) formula mb=(W/g)・R2・ω 2・L2……(2) formula On the other hand, the upper and lower and The left and right first-order unbalanced moments Wva and Mhb can be expressed using simple formulas as shown in the following formulas (3) and (4), respectively.
Mva＝mv・cos（θ＋ε） ……(3)式
Mha＝mh・sin（θ＋ε） ……(4)式
なお、mv，mhが上下および左右の最大の１次
不平衡モーメントそれぞれを示し、θが回転角度
を示すとともにεが初期位相を示す。 Mva=mv・cos(θ+ε)...Equation (3) Mha=mh・sin(θ+ε)...Equation (4) Note that mv and mh indicate the maximum vertical and horizontal first-order unbalance moments, respectively, and θ indicates the rotation angle and ε indicates the initial phase.
そこで、無補償の場合の起振モーメントである
両１次不平衡モーメントMva，Mhaを両正回転
用カウンタウエイト１５，１６および両逆回転用
カウンタウエイト１７，１８により補償し、無補
償の場合の両１次不平衡モーメントMva，Mha
それぞれを、前述の両補償用１次不平衡モーメン
トそれぞれにより打ち消して補消し、補償された
上下および左右の１次不平衡モーメントMvb，
Mhbそれぞれを零にする。 Therefore, both primary unbalanced moments Mva and Mha, which are the excitation moments in the case of no compensation, are compensated by the counterweights 15 and 16 for both forward rotations and the counterweights 17 and 18 for both reverse rotations. Both first-order unbalanced moments Mva, Mha
By canceling and compensating each of the above-mentioned first-order unbalance moments for compensation, the compensated vertical and horizontal first-order unbalance moments Mvb,
Set each Mhb to zero.
ここで、補償された上下および左右の１次不平
衡モーメントMvb，Mhbは、つぎの(5)式および
(6)式で示され、mv′，mh′それぞれが両正回転用
カウンタウエイト１５，１６および両逆回転用カ
ウンタウエイト１７，１８による両補償用１次不
平衡モーメントの最大を示し、γが前述のmv′，
mh′の初期位置を示す。 Here, the compensated vertical and horizontal first-order unbalanced moments Mvb and Mhb are expressed by the following equation (5) and
It is expressed by equation (6), where mv' and mh' respectively indicate the maximum of the first-order unbalanced moment for compensation by both forward rotation counterweights 15, 16 and both counterweights 17, 18 for reverse rotation, and γ is The aforementioned mv′,
Indicates the initial position of mh′.
Mvb＝mv・cos（θ＋ε）
＋mv′・cos（θ＋γ）＝０ ……(5)式
Mvb＝mh・sin（θ＋ε）
＋mh′・sin（θ＋γ）＝０ ……(6)式
すなわち、両正回転用カウンタウエイト１５，
１６の重量Ｗと、両逆回転用カウンタウエイト１
７，１８の重量ｗとの調整、および各カウンタウ
エイト１５，１６，１７，１８の各はずみ車４，
５，８，９への取付位置を調整し、mv′＝ma＋
mb＝β・mo，mh′＝ma−mb＝moかつ、ε＝γ
＋180゜にすることにより、(5)式および(6)式がつぎ
の(7)式および(8)式それぞれに書き換えられる。な
お、β＝mv′／mh′である。 Mvb=mv・cos(θ+ε) +mv′・cos(θ+γ)=0...Equation (5) Mvb=mh・sin(θ+ε) +mh′・sin(θ+γ)=0...Equation(6) In other words, both positive Rotating counterweight 15,
16 weight W and counterweight 1 for both reverse rotation
7, 18 with the weight w, and each counterweight 15, 16, 17, 18 each flywheel 4,
Adjust the mounting position to 5, 8, 9, mv′=ma+
mb=β・mo, mh′=ma−mb=mo and ε=γ
By setting the angle to +180°, equations (5) and (6) are rewritten into the following equations (7) and (8), respectively. Note that β=mv′/mh′.
Mvb＝mv・cos（θ＋ε）＋β・mo・cos（θ＋ε−180
゜）
＝mv・cos（θ＋ε）−β・mo・cos（θ＋ε）…
…(7)式
Mhb＝mh・sin（θ＋ε）＋mo・sin（θ＋ε−180゜）
＝mh・sin（θ＋ε）−mo・sin（θ＋ε）……(8
)式
さらに、(7)式および(8)式それぞれが常に零にな
り、無補償の場合に発生する１次不平衡モーメン
トMva，Mvbが零になることから、つぎの(9)式
および(10)式が成立する。 Mvb=mv・cos(θ+ε)+β・mo・cos(θ+ε−180
゜) = mv・cos(θ+ε)−β・mo・cos(θ+ε)…
…(7) Formula Mhb=mh・sin(θ+ε)+mo・sin(θ+ε−180°) =mh・sin(θ+ε)−mo・sin(θ+ε)……(8
) Formula Furthermore, since each of formulas (7) and (8) is always zero, and the first unbalanced moments Mva and Mvb that occur in the case of no compensation are zero, the following formulas (9) and ( 10) Equation holds true.
mv＝β・mo＝ma＋mb ……(9)式
mh＝mo＝ma−mb ……(10)式
また、(9)式および(10)式からつぎの(11)式および(12
)
式が成立する。 mv=β・mo=ma+mb...Equation (9) mh=mo=ma−mb...Equation (10) Also, from Equations (9) and (10), the following Equations (11) and (12)
)
The formula holds true.
ma＝（１＋β）・mo・（1/2） ……(11)式
mb＝（１−β）・mo・（1/2） ……(12)式
そして、第５図ａの実線に示す無補償の場合に
生じる上下の１次不平衡モーメントMvaに対し
て、同図ａの破線に示すように、上下の補償用１
次不平衡モーメントが逆モーメントとして作用
し、無補償の場合の上下の１次不平衡モーメント
が上下の補償用１次不平衡モーメントにより打ち
消されて零になる。同様に、同図ｂの実線に示す
無補償の場合に生じる左右の１次不平衡モーメン
トに対して、同図ｂの破線に示すように、左右の
補償用１次不平衡モーメントが逆モーメントとし
て作用し、無補償の場合の左右の１次不平衡モー
メントが左右の補償用１次不平衡モーメントによ
り打ち消されて零になる。 ma=(1+β)・mo・(1/2) ...Equation (11) mb=(1−β)・mo・(1/2) ...Equation (12) And as shown in the solid line in Figure 5 a For the vertical first-order unbalanced moment Mva that occurs in the case of no compensation, as shown by the broken line in Figure a,
The second-order unbalanced moment acts as a reverse moment, and the vertical first-order unbalanced moment in the case of no compensation is canceled by the first-order unbalanced moment for upper and lower compensation, and becomes zero. Similarly, for the left and right primary unbalanced moments that occur in the case of no compensation, as shown by the solid line in Figure b, the left and right compensated primary unbalanced moments act as reverse moments, as shown by the broken line in Figure b. The left and right primary unbalance moments in the case of no compensation are canceled by the left and right compensation primary unbalance moments and become zero.
したがつて、前記実施例によると、両正回転は
ずみ車４，５それぞれに重量Ｗの両正回転用カウ
ンタウエイト１５，１６それぞれを取付けるとと
もに、両逆回転はずみ車８，９それぞれに重量ｗ
の両逆回転用カウンタウエイト１７，１８それぞ
れを取り付け、両正回転歯車６，７と両逆回転歯
車１０，１１と各傘歯車１２ａ，１２ｂ，１４
ａ，１４ｂとからなる歯車機構を設けたことによ
り、デイーゼル機関１の駆動により発生する上下
および左右の１次不平衡モーメントを同時に零に
して補償することができる。 Therefore, according to the embodiment described above, both forward rotation counterweights 15 and 16 each having a weight W are attached to both forward rotation flywheels 4 and 5, respectively, and both counterweights 15 and 16 having a weight W are respectively attached to both reverse rotation flywheels 8 and 9.
Both counterweights 17 and 18 for reverse rotation are installed, and both normal rotation gears 6 and 7, both reverse rotation gears 10 and 11, and each bevel gear 12a, 12b, and 14 are installed.
By providing the gear mechanism consisting of the gears a and 14b, the vertical and horizontal primary unbalanced moments generated by the driving of the diesel engine 1 can be simultaneously reduced to zero and compensated for.
この発明は、以上説明したように構成されてい
るので、以下に記載する効果を奏する。 Since this invention is configured as described above, it produces the effects described below.
両逆回転はずみ車が、クランクシヤフトの両端
に装着された正回転はずみ車の外側に、前記シヤ
フトの軸線上の軸に設けられ、正回転はずみ車と
逆回転はずみ車が傘歯車により連結されているた
め、クランクシヤフトの回転数と同一回転数で
正、逆回転はずみ車が回転し、上下、左右の１次
不平衡モーメントを同時に補償することができ
る。 Both counter-rotating flywheels are provided on the shaft on the axis of the shaft on the outside of the normal-rotating flywheel attached to both ends of the crankshaft, and since the normal-rotating flywheel and the counter-rotating flywheel are connected by a bevel gear, the crankshaft The forward and reverse rotating flywheels rotate at the same number of rotations as the shaft, making it possible to simultaneously compensate for vertical and horizontal first-order unbalanced moments.
しかも、構成が簡単であり、かつ、クランクシ
ヤフトの軸線方向に若干容積を要しても、前記軸
線に直交する方向の容積を要さず、全体として小
形にすることができる。 Moreover, the structure is simple, and even if some volume is required in the axial direction of the crankshaft, no volume is required in the direction perpendicular to the axis, and the overall size can be made small.
第１図ないし第５図はこの発明の内燃機関の１
次不平衡モーメント補償装置の１実施例を示し、
第１図ａは正面図、同図ｂは側面図、第２図は一
部の拡大側面図、第３図は要部の斜視図、第４図
は動作説明図、第５図ａ，ｂは上下および左右の
１次不平衡モーメントの波形図、である。
３……シヤフト、４，５……正回転はずみ車、
６，７……正回転歯車、８，９……逆回転はずみ
車、１０，１１……逆回転歯車、１２ａ，１２
ｂ，１４ａ，１４ｂ……傘歯車、１５，１６……
正回転用カウンタウエイト、１７，１８……逆回
転用カウンタウエイト。
Figures 1 to 5 show one example of an internal combustion engine according to the present invention.
An example of an unbalanced moment compensator is shown,
Figure 1 a is a front view, Figure b is a side view, Figure 2 is a partially enlarged side view, Figure 3 is a perspective view of the main part, Figure 4 is an explanatory diagram of the operation, Figures 5 a and b are waveform diagrams of vertical and horizontal first-order unbalanced moments. 3...shaft, 4,5...forward rotation flywheel,
6, 7...Forward rotation gear, 8, 9...Reverse rotation flywheel, 10, 11...Reverse rotation gear, 12a, 12
b, 14a, 14b...Bevel gear, 15, 16...
Counterweight for forward rotation, 17, 18...Counterweight for reverse rotation.
Claims (1)
前記シヤフトの回転方向に回転する正回転はずみ
車と、前記シヤフトの両端の外側に前記シヤフト
の軸線上の軸にそれぞれ設けられた１個ずつの逆
回転はずみ車と、前記シヤフトの両端の前記正回
転はずみ車とそれぞれの前記逆回転はずみ車との
間にそれぞれ介在され前記正回転はずみ車に対し
前記逆回転はずみ車を逆回転させる傘歯車と、前
記両正回転はずみ車にそれぞれ取付けられた正回
転用カウンタウエイトと、前記両逆回転はずみ車
にそれぞれ取付けられた前記正回転用カウンタウ
エイトと異なる重量の逆回転用カウンタウエイト
とを備えたことを特徴とする内燃機関の１次不平
衡モーメント補償装置。1. A forward rotating flywheel that is mounted on each end of the crankshaft and rotates in the rotational direction of the shaft, and one counter-rotating flywheel that is mounted on a shaft on the axis of the shaft on the outside of both ends of the shaft, bevel gears that are interposed between the forward rotating flywheels and the respective reverse rotating flywheels at both ends of the shaft and causing the reverse rotating flywheels to rotate in the reverse direction with respect to the normal rotating flywheels; A first unbalanced moment of an internal combustion engine, comprising: a counterweight for forward rotation; and a counterweight for reverse rotation, the weight of which is different from that of the counterweight for forward rotation, which is attached to each of the two reverse rotation flywheels. Compensation device.
Priority Applications (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56083419A JPS57200744A (en) | 1981-05-30 | 1981-05-30 | Apparatus for compensating primary unbalanced moment of internal combustion engine |
| KR8202098A KR870000707B1 (en) | 1981-05-30 | 1982-05-14 | First-order balance device for an internal combustion engine |
| GB8214380A GB2099512B (en) | 1981-05-30 | 1982-05-18 | First-order balance device for an internal combustion engine |
| DE3218956A DE3218956A1 (en) | 1981-05-30 | 1982-05-19 | COMPENSATING FIRST ORDER FOR A COMBUSTION ENGINE |
| CH3286/82A CH658885A5 (en) | 1981-05-30 | 1982-05-27 | FIRST GRADE SYMMETER FOR AN INTERNAL COMBUSTION ENGINE. |
| DK240482A DK156913C (en) | 1981-05-30 | 1982-05-27 | EQUIPMENT FOR THE FIRST-ORDER OF BALANCING A BURNER ENGINE |
| NO82821790A NO159206C (en) | 1981-05-30 | 1982-05-28 | DEVICE FOR THE BALANCING OF THE FIRST ORDER OF THE FIRST ORDER IN A COMBUSTION ENGINE. |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP56083419A JPS57200744A (en) | 1981-05-30 | 1981-05-30 | Apparatus for compensating primary unbalanced moment of internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS57200744A JPS57200744A (en) | 1982-12-09 |
| JPS648221B2 true JPS648221B2 (en) | 1989-02-13 |
Family
ID=13801913
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP56083419A Granted JPS57200744A (en) | 1981-05-30 | 1981-05-30 | Apparatus for compensating primary unbalanced moment of internal combustion engine |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPS57200744A (en) |
| KR (1) | KR870000707B1 (en) |
| CH (1) | CH658885A5 (en) |
| DE (1) | DE3218956A1 (en) |
| DK (1) | DK156913C (en) |
| GB (1) | GB2099512B (en) |
| NO (1) | NO159206C (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60231042A (en) * | 1984-04-28 | 1985-11-16 | Mitsubishi Heavy Ind Ltd | Reciprocating engine |
| DE19517605C2 (en) * | 1994-05-25 | 1997-09-18 | Volkswagen Ag | Device for compensating for alternating torques and vibrations in the drive train of a motor vehicle |
| JP3346109B2 (en) * | 1995-07-31 | 2002-11-18 | ヤマハ発動機株式会社 | Internal combustion engine |
| GB2305488B (en) * | 1995-09-21 | 1999-04-28 | Moog Inc | Modular vibratory force generator, and method of operating same |
| DE19821170A1 (en) * | 1998-05-12 | 1999-11-18 | Volkswagen Ag | Crankshaft with additional mass balance, for road vehicle engine |
| GB2549294A (en) * | 2016-04-12 | 2017-10-18 | Elekta Ab | Torque reaction in rotating medical apparatus |
| US11015675B2 (en) | 2019-01-21 | 2021-05-25 | Harley-Davidson Motor Company Group, LLC | Engine balancer |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2610524A (en) * | 1948-06-23 | 1952-09-16 | Frederick K Maust | Counterbalancing device |
| JPS52132986U (en) * | 1976-04-03 | 1977-10-08 | ||
| JPS53141865A (en) * | 1977-05-17 | 1978-12-11 | Seiko Epson Corp | Oscilationproof mechanism |
-
1981
- 1981-05-30 JP JP56083419A patent/JPS57200744A/en active Granted
-
1982
- 1982-05-14 KR KR8202098A patent/KR870000707B1/en active
- 1982-05-18 GB GB8214380A patent/GB2099512B/en not_active Expired
- 1982-05-19 DE DE3218956A patent/DE3218956A1/en active Granted
- 1982-05-27 CH CH3286/82A patent/CH658885A5/en not_active IP Right Cessation
- 1982-05-27 DK DK240482A patent/DK156913C/en not_active IP Right Cessation
- 1982-05-28 NO NO82821790A patent/NO159206C/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| GB2099512A (en) | 1982-12-08 |
| NO159206B (en) | 1988-08-29 |
| JPS57200744A (en) | 1982-12-09 |
| NO821790L (en) | 1982-12-01 |
| DE3218956A1 (en) | 1982-12-16 |
| DK156913C (en) | 1990-02-26 |
| DK240482A (en) | 1982-12-01 |
| GB2099512B (en) | 1984-10-31 |
| CH658885A5 (en) | 1986-12-15 |
| DE3218956C2 (en) | 1989-09-21 |
| NO159206C (en) | 1988-12-07 |
| DK156913B (en) | 1989-10-16 |
| KR870000707B1 (en) | 1987-04-07 |
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