JPS5969550A - Gear device having eccentric mass gear - Google Patents
Gear device having eccentric mass gearInfo
- Publication number
- JPS5969550A JPS5969550A JP17752482A JP17752482A JPS5969550A JP S5969550 A JPS5969550 A JP S5969550A JP 17752482 A JP17752482 A JP 17752482A JP 17752482 A JP17752482 A JP 17752482A JP S5969550 A JPS5969550 A JP S5969550A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- center
- balancer
- crankshaft
- line
- 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.)
- Pending
Links
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
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
-
- 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
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
- F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
- F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Gear Transmission (AREA)
- Gears, Cams (AREA)
Abstract
Description
【発明の詳細な説明】
往復動型内燃機関の如く往復動てる物体を連接棒を介し
てクランク軸に連結したものでは、往復質量による慣性
力や回転質量による慣性力の不釣合いを打消ｆ ７．＝
めに、クランク軸と平行なバランサ軸を枢支し、同バラ
ンサ軸にバランサＥ 一体ＩＣ設けたものがあるが、バ
ランサ軸およびバランサを収納するための特別な空間を
必要とし、また部品点数が増加し、回転部分の増加によ
り摩擦ロスが増大する等の欠点があった。[Detailed Description of the Invention] In a reciprocating internal combustion engine in which a reciprocating object is connected to a crankshaft via a connecting rod, the unbalance of the inertial force due to the reciprocating mass and the inertial force due to the rotating mass is canceled out. ．． =
For this purpose, there is a balancer shaft that is parallel to the crankshaft and a balancer E integrated IC installed on the balancer shaft, but this requires a special space to accommodate the balancer shaft and balancer, and the number of parts is large. There were disadvantages such as an increase in friction loss due to an increase in the number of rotating parts.
コｏ）ような欠点を除去するために、クランク軸および
同クランク軸と平行な軸に歯数および歯形が同一な歯車
を嵌着するとともに、同平行軸に嵌着ざ旧、た歯車に、
前記慣性力の不釣合いを打消すに足る偏心質量を与えた
ものがあるが、偏心質量歯車はその偏心質量により遠心
力が発生し、その偏心遠心力により偏心質量歯車は偏心
運動を起し、クランク軸と一体の歯車と偏心質量歯■と
は正常に噛み合わなくなる。o) In order to eliminate such defects, gears with the same number of teeth and tooth profile are fitted to the crankshaft and a shaft parallel to the crankshaft, and gears that are not fitted to the same parallel shaft,
Some gears are provided with an eccentric mass sufficient to cancel out the unbalance of the inertial force, but the eccentric mass gear generates centrifugal force due to its eccentric mass, and the eccentric centrifugal force causes the eccentric mass gear to eccentrically move. The gear that is integral with the crankshaft and the eccentric mass teeth ■ do not mesh properly.
第１図ないし第２図を参照してこｎを具体的に説明する
。This will be specifically explained with reference to FIGS. 1 and 2.
第１図に図示されるように偏心ウェイト０３が駆動側歯
車Ｏ１に摺近した状態では、その偏心ウェイト０３の遠
心力ｍｒｕ＞２（ｍ：偏心ウェイトの質量、ｒ：偏心ウ
ェイト歯車の中心と偏心ウェイトの重心との距離、−二
偏心ウエイト歯車の角速度）により偏心ウェイト歯車０
２が駆動側歯車Ｏ１に接近し、バックラッシュが小ぎく
なってｏ念り音および歯面ピッチングの発生原因となり
、ま１−第２図に図示す２１するように偏心ウェイ）０
３か駆動側歯車０１に対して直径上反対側に位ｆｆｉ
した状態では、その遠心力ｍｒＩＩＪ２により偏心ウェ
イト歯車０２が駆動側歯車０１より離れる方向へ移動し
、ノ々ツクラッシュが大きくなって歯車の打たかれ音が
発生′１−る。As shown in FIG. 1, when the eccentric weight 03 is sliding close to the driving gear O1, the centrifugal force mru of the eccentric weight 03>2 (m: mass of the eccentric weight, r: center of the eccentric weight gear The eccentric weight gear is 0 due to the distance from the center of gravity of the eccentric weight, - the angular velocity of the two eccentric weight gears.
2 approaches the drive side gear O1, and the backlash becomes small, causing noise and pitching of the tooth surface.
3 or located on the diametrically opposite side to drive side gear 01 ffi
In this state, the centrifugal force mrIIJ2 moves the eccentric weight gear 02 in a direction away from the driving gear 01, and the notch crash increases, producing a gear hitting sound '1-.
しかも歯車０１．０２間の噛み合い状態が周期的に変化
するため、振動が発生し易い。Moreover, since the meshing state between the gears 01 and 02 changes periodically, vibrations are likely to occur.
本発明はこのような不都合？解消した平行歯ＩＪＺ装置
の改良に係り、その目的とする処は、噛み合い状態が一
定で騒音、振動が発生しない歯車装置を供する点にある
。Does the present invention have such inconveniences? The purpose of improving the parallel tooth IJZ device is to provide a gear device that has a constant meshing state and does not generate noise or vibration.
以下第３図ないし第６図に図示ヒＴ１．た本発明の一実
施例について説明する。Below, in FIGS. 3 to 6, T1. An embodiment of the present invention will be described.
１はエンジンのクランク軸で、同クランク軸１はベアリ
ング２を介してクランクケース３に回転自在に枢支ぎれ
ている。1 is a crankshaft of an engine, and the crankshaft 1 is rotatably supported by a crankcase 3 via a bearing 2.
また前記クランク軸１に隣接しこｎと平行にバランサ軸
４がベア１）”／グ５を介してクランクケース３に回転
自在に枢支ぎれている。Further, a balancer shaft 4 adjacent to and parallel to the crankshaft 1 is rotatably supported on the crankcase 3 via a bear 1)''/g 5.
ざらに前記クランク軸１の両端または一端にバランサド
ライブ歯車６が一体に嵌着されるとともに八これと同一
歯数のバランサドリブン歯！ ７７）ｉ前記バランサ１
ｌｌｌ ４の両端まだは一端に一体に嵌着され、両歯車
６．７は相互に噛み合わぎれている。Roughly speaking, the balancer drive gear 6 is integrally fitted to both ends or one end of the crankshaft 1, and has eight balancer driven teeth with the same number of teeth! 77) i Said balancer 1
Both ends of Ill 4 are fitted together with one end, and both gears 6.7 are meshed with each other.
ざらにバランサドリブン歯車７１ｃは偏心ウェイト８が
一体（（形成されている。The balancer driven gear 71c is integrally formed with the eccentric weight 8.
しかしてエンジンの１次の不平衡慣性力と不平衡慣性偶
力とが同時に消去されるような位置関係・に前記バラン
サドリブン歯車７はバランサドライブ歯Ｔｉ、６に噛み
合わさｎでいる。Thus, the balancer driven gear 7 is meshed with the balancer drive teeth Ti, 6 in a positional relationship such that the primary unbalanced inertia force and the unbalanced inertia couple of the engine are simultaneously eliminated.
また前記４（ランサドリブン歯■７においてＣま、第５
１如に図示されるように、歯車７の中心０から歯■７の
重心Ｏｗに向けて結んだ延長線ＯＸ付近のまたぎ歯厚を
Ａ１歯■中心０を通り前記延長線Ｏｘに対して直角な線
ＯＹ付近のまたぎ歯厚をＢ・歯車中心Ｏから歯車７の重
心Ｏｗと反対方向に向いた線０２付近のまたぎ歯厚をＯ
（！ニーｆると、Ａ＜Ｅ＜Ｃ
なる関係が成立するように、バランサドリブン歯１“°
””＜ｕａａ””パ′° へこのようなＡｌ
１形に形成するには、通常の創■歯切法または成形歯切
法により歯切加工を行ない、このように形成されたバラ
ンサドリブン歯車７とンエービソグカッターとをエンジ
ンの実際の回転角速度ωにて回転させてその遠心力ｍｒ
の２によりバランサドリブン歯車７を撓わませながらシ
ェービング加工を行えばよい。In addition, in the above-mentioned 4 (lancer driven tooth
As shown in Figure 1, the thickness of the straddle tooth near the extension line OX drawn from the center 0 of the gear 7 to the center of gravity Ow of the tooth 7 is at right angles to the extension line Ox, passing through the center 0 of the gear A1. The thickness of the straddle tooth near the line OY is B. The thickness of the straddle tooth near the line 02 facing in the opposite direction from the gear center O to the center of gravity Ow of gear 7 is O.
(! When knee f, the balancer driven tooth 1"°
""<uaa""Pa'° to Al like this
To form one shape, gear cutting is performed using the normal wound gear cutting method or forming gear cutting method. Rotating at angular velocity ω, the centrifugal force mr
2, the shaving process may be performed while the balancer driven gear 7 is deflected.
または通常の創成歯切法２行なう場合に、偏心ウェイト
８の遠心力ｍｒＬＡＩ＋！によるバランサドリブンｆｆ
４車７の変位に対応させて、被切削加工物たるバランサ
ドリブン歯車７を歯車中心ＯよりＯｘ方向へ変位させた
状態で、歯切加工を行なえばよい。Or when performing the normal generation gear cutting method 2, the centrifugal force mrLAI+ of the eccentric weight 8! Balancer driven FF by
Gear cutting may be performed while the balancer driven gear 7, which is the workpiece to be cut, is displaced from the gear center O in the Ox direction in accordance with the displacement of the four wheels 7.
第３図ないし第６図に図示の実施例は前記したように構
ｔｊＪ’ｇ ｎ、ているので、前記バランサドリブン歯
車７の偏心ウェイト８により、エンジンの１次の不平衡
慣性力と不平衡慣性偶力とが同時に消去さハる。Since the embodiment shown in FIGS. 3 to 6 is constructed as described above, the eccentric weight 8 of the balancer driven gear 7 causes the unbalanced inertia force of the engine to be unbalanced. The inertia couple is eliminated at the same time.
また第１図に図示されるように、ノ（ランサドリブン歯
車７の中心より偏心ウェイト８への延長線ＯＸ力Ｓバラ
ンサドライブ歯匝６の中心に指向した時においては、偏
心ウェイト８の遠心力ｍｒｖＪによりバランサドリブン
歯車７がバランサドライブ歯Ｍｆ、 ６に接近するよう
に変位しても、バランサドライブ歯車６に噛み合ってい
るバランサドリブン歯車７のまたぎ歯厚Ａがこわと直角
な位置関係のまたぎ歯厚Ｂに比べて小さくなっているた
め、バックラッシュは変らず 、、ｔ、り音力５発生す
ることがなし）。In addition, as shown in FIG. Even if the balancer driven gear 7 is displaced to approach the balancer drive tooth Mf, 6 due to mrvJ, the straddle tooth thickness A of the balancer driven gear 7 meshing with the balancer drive gear 6 is stiff and the straddle tooth is in a positional relationship perpendicular to the stiffness. Since it is smaller than the thickness B, the backlash remains unchanged and no sound force is generated.
ざらに第２図に図示されるように、バランサドリブン歯
車７の中心より偏心ウェイト８の反対側への延長ｉｏｚ
がバランサドライブ歯車６の中心に指向した時において
は、偏心ウェイト８の遠心力ｍｒ（Ｊ’によりバランサ
ドリブン歯■７がバランサドライブ歯車６より離れるよ
うに変位しても、バランサドライブ歯ｍ６に噛み合って
いるバランサドリブン歯車７のまたぎ歯厚Ｃがこれと直
角な位置関係のまたぎ歯厚Ｂに比べて大きくなっている
ため、バックラツンユは変らず、歯車の打たかれ音が発
生しない。As roughly illustrated in FIG. 2, the eccentric weight 8 extends from the center of the balancer driven gear 7 to the opposite side.
is directed toward the center of the balancer drive gear 6, even if the balancer driven tooth 7 is displaced away from the balancer drive gear 6 due to the centrifugal force mr (J' of the eccentric weight 8), it will mesh with the balancer drive tooth m6. Since the straddle tooth thickness C of the balancer driven gear 7 is larger than the straddle tooth thickness B of the balancer driven gear 7 in a positional relationship perpendicular to the straddle tooth thickness, the back rattle does not change and gear striking noise does not occur.
このように前記実施例においては、バランサドリブン歯
車７はバランサドライブ歯車６に対して常ＶＣ一定のバ
ックラツンユで噛み合っているため、然に防止すること
ができる。As described above, in the above embodiment, the balancer driven gear 7 meshes with the balancer drive gear 6 with a constant VC backlash, so that this problem can be prevented.
第３図ないし第６図に図示の実施例は、エンジンのバラ
ンサに発明を適用したものであるが、１対または複数対
の偏心重錘を互に逆方向に回転ぎせる７Ｊｒ振機等１（
も勿論適用可能である。The embodiments shown in FIGS. 3 to 6 are those in which the invention is applied to an engine balancer. (
Of course, it is also applicable.
本発明では、歯車重心が回転中心線上にない平行軸歯Ｊ
１￥において、回転中心線から重心に向けて結んだ延長
線付近のまたぎ歯厚をＡ１回転中心線を通り前記延長線
に対して直角な線付近のまたぎ歯厚をＢ１重心から回転
中心線に向けて結んだ延長線付近０）重たぎ歯厚をＣと
すると、Ａ＜Ｂ＜Ｃ
なる関係が成立てるように偏心質量歯車の歯２形成した
だめ、前記偏心質量歯車と普通の歯車とを噛み合せて回
転ぎせた場合、同偏心質量歯車に遠心力が働いて両歯車
の中心距離が周期的に変動しても、両歯車の噛み合い状
態は一定となり、騒音、振動等の発生を未然に防止する
ことができる。In the present invention, the parallel axis tooth J whose center of gravity of the gear is not on the rotation center line
At 1 yen, the thickness of the straddle tooth near the extension line drawn from the rotation center line toward the center of gravity is the thickness of the straddle tooth near the line that passes through the A1 rotation center line and is perpendicular to the extension line from the B1 center of gravity to the rotation center line. 0) Near the extension line connected toward the direction 0) If the thickness of the heavy gear tooth is C, the teeth 2 of the eccentric mass gear are formed so that the relationship A<B<C is established. When the gears are meshed and rotated, even if centrifugal force acts on the eccentric mass gears and the distance between the centers of both gears changes periodically, the meshing state of both gears remains constant, preventing the occurrence of noise, vibration, etc. It can be prevented.
第１図および第２図は偏心質量歯車と普通の歯■とが噛
み合って回転している状態を示したもので、第１図はそ
の偏心質量による遠心力で両歯車間の距離が接近し、第
２図は離隔した状態を示しており、第３図は不発１９１
に係る偏心質量歯車を有てる歯車装置の一実施例を図示
した側面図、第４図は第３図のＩＶ −ＩＶ線に沿って
裁断した縦断平面図、第５図はその要部拡大側面図、第
６図はその縦断面図である。
１・・・クランク軸、２・・・ベアリング、３・・・ク
ランクケース、４・・・バラン→ｆ軸、５・・・ベアリ
ング、６・・・バランサドライブ歯車、７・・・バラン
サドリブン歯車、８・・・偏心ウェイト。
代理人 弁理士 江 原 望 外１名罵４図
ム
笛５図
策６図
３０２−Figures 1 and 2 show a state in which an eccentric mass gear and a normal tooth are meshing and rotating, and in Figure 1, the distance between both gears approaches due to the centrifugal force caused by the eccentric mass. , Figure 2 shows the isolated state, and Figure 3 shows the unexploded 191
FIG. 4 is a longitudinal cross-sectional plan view taken along the line IV-IV in FIG. 3, and FIG. 5 is an enlarged side view of the main parts thereof. FIG. 6 is a longitudinal sectional view thereof. 1... Crankshaft, 2... Bearing, 3... Crankcase, 4... Balun → f axis, 5... Bearing, 6... Balancer drive gear, 7... Balancer driven gear , 8... Eccentric weight. Agent Patent attorney Nozomu Ehara and 1 other person 4 Figure 5 Whistle 5 Strategy 6 Figure 302-
Claims (1)
転中心線から重心に向けて結んだ延長線付近のまたぎ歯
厚をＡ１回転中心線を通り前記延長線に対して直角な線
付近のまたぎ歯厚をＢ１重心から回転中心線に向けて結
んだ延長線イ」近のまたぎ歯厚をＣとすると、 Ａ＜Ｂ＜Ｃ なる関係が成立するように、偏心質量歯車の歯を形成し
たことを特徴とする偏心質量歯車を有する歯車装置。[Scope of Claims] In a parallel shaft gear whose gear center of gravity is not on the rotation center line, the straddle tooth thickness near the extension line drawn from the rotation center line toward the center of gravity is perpendicular to the extension line passing through the A1 rotation center line. If the thickness of the straddle tooth near the line B1 is an extension of the line A drawn from the center of gravity toward the center of rotation, then C is the thickness of the straddle tooth near the line B1. A gear device having an eccentric mass gear formed with teeth.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17752482A JPS5969550A (en) | 1982-10-12 | 1982-10-12 | Gear device having eccentric mass gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17752482A JPS5969550A (en) | 1982-10-12 | 1982-10-12 | Gear device having eccentric mass gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS5969550A true JPS5969550A (en) | 1984-04-19 |
Family
ID=16032423
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17752482A Pending JPS5969550A (en) | 1982-10-12 | 1982-10-12 | Gear device having eccentric mass gear |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5969550A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7506627B2 (en) * | 2004-08-17 | 2009-03-24 | Yamaha Motor Co., Ltd. | Balancer shaft arrangement for engine |
-
1982
- 1982-10-12 JP JP17752482A patent/JPS5969550A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7506627B2 (en) * | 2004-08-17 | 2009-03-24 | Yamaha Motor Co., Ltd. | Balancer shaft arrangement for engine |
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