JPS58126434A - Smoothing device of torque in internal-combustion engine - Google Patents
Smoothing device of torque in internal-combustion engineInfo
- Publication number
- JPS58126434A JPS58126434A JP977082A JP977082A JPS58126434A JP S58126434 A JPS58126434 A JP S58126434A JP 977082 A JP977082 A JP 977082A JP 977082 A JP977082 A JP 977082A JP S58126434 A JPS58126434 A JP S58126434A
- Authority
- JP
- Japan
- Prior art keywords
- motor
- crankshaft
- torque
- generator
- combustion engine
- 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
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/06—Engines with means for equalising torque
Abstract
Description
【発明の詳細な説明】
この発明は、例えば単気筒又は2〜3気筒の小数気筒内
燃機関のトルク変動を平滑化イ゛る装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for smoothing torque fluctuations in, for example, a single cylinder or 2 to 3 cylinder internal combustion engine.
従来のこの種のトルク平滑化装置としては、例えば内燃
機関(以下「エンジンJと言う)のクランク軸の後端に
大型のフライホイールを取り付けたものや、「機械の研
究j第25巻第1号(1973)の116頁に記載され
ているようにバラン1−
スウエイトも用いたもの等がある。Conventional torque smoothing devices of this type include, for example, those in which a large flywheel is attached to the rear end of the crankshaft of an internal combustion engine (hereinafter referred to as "Engine J"), and those in "Machine Research J Vol. 25, No. 1 As described on page 116 of No. (1973), there are also those using balun 1-thwaite.
しかしながら、このような従来のトルク平滑化装置にあ
っては、フライホイール乃至バランスウェイトの慣性モ
ーメントIPを利用して、その蓄積エネルギによって、
トルクを平滑化するようにしているため、平滑効果を大
きくするには、慣性モーメントIPi大きくしなければ
ならず、それによって、装置の重量が増加したり、エン
ジンの加減速に対する応答性が悪化したりする問題があ
った。However, in such a conventional torque smoothing device, the moment of inertia IP of the flywheel or balance weight is used, and the accumulated energy is used to
Since the torque is smoothed, in order to increase the smoothing effect, the moment of inertia IPi must be increased, which increases the weight of the device and worsens the response to acceleration and deceleration of the engine. There were some problems.
なお、バランスウェイトラ用いたものでは、振動の減少
には大きな効果があるが、トルク変動の吸収にはフライ
ホイール以上の効果はない。It should be noted that although balance weighters are highly effective in reducing vibration, they are not as effective as flywheels in absorbing torque fluctuations.
この発明は、このような従来の間顕点に着目してなされ
たもので、電磁気力を利用して、エネルギの吸収、放出
を行なわせる言わば能動的(アクティブ)フライホイー
ルを用いて前述の問題を解消した内燃機関のトルク平滑
化装置を提供することを目的とする。This invention was made by focusing on such conventional problems, and it solves the above-mentioned problem by using an active flywheel that absorbs and releases energy using electromagnetic force. An object of the present invention is to provide a torque smoothing device for an internal combustion engine that eliminates the problem.
そのため、この発明による内燃機関のトルク平2−
消化装置は、レシプロ(往復動)式の内燃機関のクラン
ク軸に接続した電動機及び発電機として動作し得る電久
機械と、内燃機関の1ザイクル中の圧縮、爆発、吸排気
の各行程に応じて前記電気機械の電動機動作と発動機動
作とを切り替えて内燃機関のトルク変動を小さくする制
御回路とによって構成している。Therefore, the torque extinguisher for an internal combustion engine according to the present invention has an electric machine that can operate as an electric motor and a generator connected to the crankshaft of a reciprocating (reciprocating) internal combustion engine, and a The internal combustion engine is configured with a control circuit that reduces torque fluctuations of the internal combustion engine by switching between electric motor operation and engine operation of the electric machine according to the compression, explosion, and intake/exhaust strokes of the internal combustion engine.
以下、この発明の実施例全添付図面を参照して説明する
。Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.
第1図は、この発明の一実施例を示す構成図である。FIG. 1 is a block diagram showing an embodiment of the present invention.
同図において、単筒エンジン1のクランク軸1aには、
電動機及び発電機として動作し得る電気機械である大径
偏平型の直流モータ2を、通常フライホイールを取り付
ける位置に直結している。In the figure, the crankshaft 1a of the single-cylinder engine 1 includes:
A large-diameter flat DC motor 2, which is an electric machine that can operate as an electric motor and a generator, is directly connected to a position where a flywheel is normally attached.
すなわち、エンジン1のクランク軸1aとモー ・り
2の出力軸6とは一体となって回転する。That is, the crankshaft 1a of the engine 1 and the output shaft 6 of the motor 2 rotate together.
制御回路4は、図示しないクランク角センサや絞り弁開
度センサ等から入力されるクランク角データや絞り弁開
度データ等に基づいて、エンジン′ 1の1ザイクル中
の圧縮、爆発(膨張)、吸排気の各行程を検知して、そ
の検知結果に応じて蓄電器5から電力をモータ2に供給
してモータ2を電動機として動作させたり、逆に電力供
給を停止して、クランク軸12によって回転されて発電
機として動作するモータ2から発生する電力を蓄電器5
に蓄えたりする。The control circuit 4 controls compression, explosion (expansion), etc. during one cycle of the engine '1 based on crank angle data, throttle valve opening data, etc. input from a crank angle sensor, throttle valve opening sensor, etc. (not shown). Each intake and exhaust stroke is detected, and depending on the detection result, power is supplied from the capacitor 5 to the motor 2 to operate the motor 2 as an electric motor, or conversely, the power supply is stopped and the motor is rotated by the crankshaft 12. The electric power generated from the motor 2, which operates as a generator, is transferred to a power storage device 5.
I store it in.
通常の単筒エンジンは、第2図(イ)に実線で示すよう
に1サイクル(4ザイクルエンジンではクランク軸2回
転720°)中にクランク軸の角速度ωが大きく変動す
る(4ストローク・1サイクルエンジンでは、1ザイク
ル中にクランク軸1aが2回転する)。In a normal single-cylinder engine, the angular velocity ω of the crankshaft fluctuates greatly during one cycle (2 revolutions of the crankshaft at 720° in a 4-cycle engine), as shown by the solid line in Figure 2 (A) (4 strokes/1 cycle). In the engine, the crankshaft 1a rotates twice during one cycle).
すなわち圧縮行程では、フライホイールのエネルギを消
費しながら筒内のガスを圧縮するから、この間のクラン
ク軸の角速度は減少を続ける。That is, in the compression stroke, the gas in the cylinder is compressed while consuming the energy of the flywheel, so the angular velocity of the crankshaft continues to decrease during this period.
爆発(膨張)行程では、燃焼ガスがピストンを押し下げ
てフライホイールを加速するから、角速度ωは大きくな
る。During the explosion (expansion) stroke, the combustion gas pushes down the piston and accelerates the flywheel, so the angular velocity ω increases.
排気、吸入の両行程では、前述の2つの行程はどの大幅
な変化はないが、ピストン等のフリクション(摩擦)仕
事やポンピング仕事の分のエネルギを失うため、角速度
ωは低下を続ける。In both the exhaust and intake strokes, although there is no significant change in the two strokes mentioned above, the angular velocity ω continues to decrease because energy is lost due to the friction work of the piston, etc. and the pumping work.
そこで、上記行程において、第1図に示す単筒エンジン
1のクランク軸1aの角速度ωが低下する吸排気行程及
び圧縮行程では制御回路4は蓄電器5からモータ2に電
力を供給して、モータ2ff:電動機として動作させ、
このモータ2の駆動力によってクランク軸1aの角速度
ωの低下を抑え、又爆発(膨張)行程のように角速度ω
が急増するところでは、制御回路4はモータ2への給電
を停止して、モータ2を発電機として動作させるため、
クランク軸1aの回転エネルギの一部はモータ2を回転
させるための仕事に消費されるようになる。Therefore, in the above strokes, in the intake and exhaust strokes and compression strokes in which the angular velocity ω of the crankshaft 1a of the single-cylinder engine 1 shown in FIG. : Operates as an electric motor,
The driving force of the motor 2 suppresses the decrease in the angular velocity ω of the crankshaft 1a, and also prevents the angular velocity ω from decreasing as in the explosion (expansion) stroke.
When the power increases rapidly, the control circuit 4 stops power supply to the motor 2 and causes the motor 2 to operate as a generator.
A part of the rotational energy of the crankshaft 1a is consumed for work for rotating the motor 2.
それによって、角速度ωの増加を抑えることができるの
で、クランク軸1aの角速度ωは、第2図(イ)に破線
で示すようにほぼ一定になり、エンジン1の発生トルク
も均一になる。As a result, an increase in the angular velocity ω can be suppressed, so that the angular velocity ω of the crankshaft 1a becomes approximately constant as shown by the broken line in FIG. 2(A), and the torque generated by the engine 1 also becomes uniform.
なお、第2図(ロ)はクランク位置に対応するモータ2
の発生トルクを示す。ここで、トルクが負というのは、
モータ2が発電機として動作して、エンジン1に制動を
かけている事を示している。In addition, Fig. 2 (b) shows the motor 2 corresponding to the crank position.
shows the generated torque. Here, negative torque means
This shows that the motor 2 operates as a generator and applies braking to the engine 1.
第3図は、この発明の他の実施例を示す構成図であり、
第1図と対応する部分には同一符号を付してその部分の
説明を省略する。FIG. 3 is a configuration diagram showing another embodiment of the present invention,
Portions corresponding to those in FIG. 1 are designated by the same reference numerals, and explanations of those portions will be omitted.
この実施例では、モータ2をクランク軸1aに直接取り
付けず、例えばエンジン1に取り付けておいて、クラン
ク軸1aとモータ2の出力軸乙に夫々取り付けられて互
いに噛み合う大歯車6と小歯車7とからなる増速機によ
って両者を連結している。In this embodiment, the motor 2 is not directly attached to the crankshaft 1a, but is attached to the engine 1, for example, and a large gear 6 and a small gear 7 are attached to the crankshaft 1a and the output shaft B of the motor 2, respectively, and mesh with each other. The two are connected by a speed increaser consisting of.
このようにすると、前実施例と同様な効果に加えて次の
ような利点がある。By doing so, in addition to the same effects as in the previous embodiment, there are the following advantages.
■ モータ2として高速型のものを使用できるため、モ
ータ2を小型軽量化できる。- Since a high-speed motor can be used as the motor 2, the motor 2 can be made smaller and lighter.
■ モータ2の発生又は吸収トルクを小さくできるため
、やはりモータ2を小型、軽量化でき、特にモータ2の
径方向の寸法を小型化できる。(2) Since the generated or absorbed torque of the motor 2 can be reduced, the motor 2 can also be made smaller and lighter, and in particular, the radial dimension of the motor 2 can be made smaller.
ただし、歯車機構の分だけ第1図の実施例より構成が複
雑で重くなるため、装置の配置を工夫する必要がある。However, since the structure is more complicated and heavier than the embodiment shown in FIG. 1 due to the gear mechanism, it is necessary to devise the arrangement of the device.
また、l・ルクが正負頻繁に反転するため、歯車6.7
のバックラッシュ対策等歯車の設計に留意する必要があ
る。In addition, since l・lux frequently reverses positive and negative, gear 6.7
It is necessary to pay attention to gear design such as backlash countermeasures.
なお、−上記各実施例では、この発明を単筒エンジンに
適用した例について述べたが、2気筒又は3気筒エンジ
ン等にも同様に適用できろものである。In the above embodiments, the present invention was applied to a single-cylinder engine, but it can be similarly applied to a two-cylinder or three-cylinder engine.
以」二説明してきたように、この発明による内燃機関の
トルク平滑化装置は、従来のように慣性モーメン)IP
に依存した受動的なトルクの平滑化ではなく、モータ/
ジェネレータを使用した能動的なトルクの平滑化を行な
うようにしたので、装置自体の小型・軽量化が計れるば
かりか、内燃機関の加減速等のトランジェント(過渡)
時の応答が速(なる。As has been explained hereafter, the torque smoothing device for an internal combustion engine according to the present invention is capable of reducing the moment of inertia)
rather than passive torque smoothing that relies on motor/
Active torque smoothing using a generator not only makes the device itself smaller and lighter, but also reduces transients such as acceleration and deceleration of internal combustion engines.
Time response is fast.
第1図は、この発明の一実施例を示す構成図、第2図(
イ)、(ロ)は、夫々第1図の動作説明に供する線図、
第3図は、この発明の他の実施例を示す構成図である。
1・・・・・・単筒エンジン 1a・・・・・・クラ
ンク軸2・・・・・・モータ(電気機械)
6・・・・・・出力軸 4・・・・・・制御回
路5・・・・・・蓄電器 6,7・・・・・・歯車
第1図
(イ)
/′
Q
(ロ)
クランク角データ
絞り弁開度データ 市In回路 4その
第2図
ク
ン
ク
軸
の
角
速
度
■
クランク角FIG. 1 is a block diagram showing an embodiment of the present invention, and FIG. 2 (
A) and (B) are diagrams for explaining the operation of FIG. 1, respectively. FIG. 3 is a configuration diagram showing another embodiment of the present invention. 1... Single cylinder engine 1a... Crankshaft 2... Motor (electric machine) 6... Output shaft 4... Control circuit 5・・・・・・Condenser 6, 7・・・・Gear Diagram 1 (A) /' Q (B) Crank angle data Throttle valve opening data City In circuit 4 Part 2 Diagram angular velocity of Kunk shaft ■ crank angle
Claims (1)
及び発電機として動作し得る電気機械と、前記内燃機関
の1サイクル中の圧縮、爆発、吸排気の各行程に応じて
前記電気機械の電動機動作と発電機動作とを切り替えて
前記(ハ)燃機関のトzレク変動を小さくする制御回路
とによって構成したことを特徴とする内燃機関のトルク
平滑化装置。1 An electric machine that can operate as a motor and a generator connected to the crankshaft of a reciprocating internal combustion engine, and a motor operation of the electric machine according to each stroke of compression, explosion, intake and exhaust during one cycle of the internal combustion engine. A torque smoothing device for an internal combustion engine, comprising: (c) a control circuit that reduces torque fluctuations of the combustion engine by switching between the generator operation and the generator operation.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP977082A JPS58126434A (en) | 1982-01-23 | 1982-01-23 | Smoothing device of torque in internal-combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP977082A JPS58126434A (en) | 1982-01-23 | 1982-01-23 | Smoothing device of torque in internal-combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS58126434A true JPS58126434A (en) | 1983-07-27 |
Family
ID=11729494
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP977082A Pending JPS58126434A (en) | 1982-01-23 | 1982-01-23 | Smoothing device of torque in internal-combustion engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58126434A (en) |
Cited By (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60119330A (en) * | 1983-11-30 | 1985-06-26 | Nissan Motor Co Ltd | Torque variation controller for internal-combustion engine |
JPS6161922A (en) * | 1984-08-31 | 1986-03-29 | Mazda Motor Corp | Engine torque fluctuation controller |
EP0175952A2 (en) * | 1984-08-31 | 1986-04-02 | Mazda Motor Corporation | Means for suppressing engine output torque fluctuations |
JPS61149539A (en) * | 1984-12-21 | 1986-07-08 | Nissan Motor Co Ltd | Torque fluctuation restricting device for engine |
JPS61200333A (en) * | 1985-03-01 | 1986-09-04 | Nissan Motor Co Ltd | Torque fluctuation restraining device for engine |
JPS62153529A (en) * | 1985-12-27 | 1987-07-08 | Isuzu Motors Ltd | Torque fluctuation suppressing device for internal combustion engine |
JPS63212723A (en) * | 1987-02-27 | 1988-09-05 | Hitachi Ltd | Torque control device of internal combustion engine |
WO1995023301A1 (en) * | 1994-02-28 | 1995-08-31 | Clouth Gummiwerke Ag | Process and device for active vibration damping |
WO1997008437A1 (en) | 1995-08-31 | 1997-03-06 | Isad Electronic Systems Gmbh & Co. Kg | Drive system, in particular a drive system for a motor vehicle, and method of operating the system |
WO1997008477A3 (en) * | 1995-08-31 | 1997-08-14 | Clouth Gummiwerke Ag | System for actively reducing radial vibrations in a rotating shaft, and method of operating the system to achieve this |
WO1998039579A2 (en) | 1997-03-06 | 1998-09-11 | Isad Electronic Systems Gmbh & Co. Kg | Device for reducing rotational irregularities and method relating thereto |
US5939793A (en) * | 1994-02-28 | 1999-08-17 | Isad Electronic Systems Gmbh & Co. Kg | Starter for drive units, especially internal combustion engines, and process for operating the same |
US6202776B1 (en) * | 1995-08-31 | 2001-03-20 | Isad Electronic Systems Gmbh & Co. Kg | Drive system, especially for a motor vehicle, and method of operating same |
US6487998B1 (en) * | 1995-08-31 | 2002-12-03 | Isad Electronic Systems Gmbh & Co., Kg | Drive system, particularly for a motor vehicle, and process for operating it |
US6588392B2 (en) * | 2001-08-17 | 2003-07-08 | Delphi Technologies, Inc. | Fuel efficient powertrain system |
WO2010106560A1 (en) * | 2009-03-19 | 2010-09-23 | Alenia Aeronautica S.P.A. | Starting and electricity generating system for a reciprocating engine |
US8496079B2 (en) | 2009-09-16 | 2013-07-30 | Swissauto Powersport Llc | Electric vehicle and on-board battery charging apparatus therefore |
WO2014002845A1 (en) * | 2012-06-29 | 2014-01-03 | 株式会社マキタ | Power device for portable working machine, and portable working machine |
US10744868B2 (en) | 2016-06-14 | 2020-08-18 | Polaris Industries Inc. | Hybrid utility vehicle |
US10780770B2 (en) | 2018-10-05 | 2020-09-22 | Polaris Industries Inc. | Hybrid utility vehicle |
US11370266B2 (en) | 2019-05-16 | 2022-06-28 | Polaris Industries Inc. | Hybrid utility vehicle |
-
1982
- 1982-01-23 JP JP977082A patent/JPS58126434A/en active Pending
Cited By (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60119330A (en) * | 1983-11-30 | 1985-06-26 | Nissan Motor Co Ltd | Torque variation controller for internal-combustion engine |
US4699097A (en) * | 1984-08-31 | 1987-10-13 | Mazda Motor Corporation | Means for suppressing engine output torque fluctuations |
JPS6161922A (en) * | 1984-08-31 | 1986-03-29 | Mazda Motor Corp | Engine torque fluctuation controller |
EP0175952A2 (en) * | 1984-08-31 | 1986-04-02 | Mazda Motor Corporation | Means for suppressing engine output torque fluctuations |
JPS61149539A (en) * | 1984-12-21 | 1986-07-08 | Nissan Motor Co Ltd | Torque fluctuation restricting device for engine |
JPS61200333A (en) * | 1985-03-01 | 1986-09-04 | Nissan Motor Co Ltd | Torque fluctuation restraining device for engine |
JPS62153529A (en) * | 1985-12-27 | 1987-07-08 | Isuzu Motors Ltd | Torque fluctuation suppressing device for internal combustion engine |
JPS63212723A (en) * | 1987-02-27 | 1988-09-05 | Hitachi Ltd | Torque control device of internal combustion engine |
US5033425A (en) * | 1987-02-27 | 1991-07-23 | Hitachi, Ltd. | Internal combustion engine equipped with a torque controller |
WO1995023301A1 (en) * | 1994-02-28 | 1995-08-31 | Clouth Gummiwerke Ag | Process and device for active vibration damping |
US5939793A (en) * | 1994-02-28 | 1999-08-17 | Isad Electronic Systems Gmbh & Co. Kg | Starter for drive units, especially internal combustion engines, and process for operating the same |
WO1997008437A1 (en) | 1995-08-31 | 1997-03-06 | Isad Electronic Systems Gmbh & Co. Kg | Drive system, in particular a drive system for a motor vehicle, and method of operating the system |
WO1997008477A3 (en) * | 1995-08-31 | 1997-08-14 | Clouth Gummiwerke Ag | System for actively reducing radial vibrations in a rotating shaft, and method of operating the system to achieve this |
US6487998B1 (en) * | 1995-08-31 | 2002-12-03 | Isad Electronic Systems Gmbh & Co., Kg | Drive system, particularly for a motor vehicle, and process for operating it |
US6202776B1 (en) * | 1995-08-31 | 2001-03-20 | Isad Electronic Systems Gmbh & Co. Kg | Drive system, especially for a motor vehicle, and method of operating same |
WO1998039579A2 (en) | 1997-03-06 | 1998-09-11 | Isad Electronic Systems Gmbh & Co. Kg | Device for reducing rotational irregularities and method relating thereto |
US6588392B2 (en) * | 2001-08-17 | 2003-07-08 | Delphi Technologies, Inc. | Fuel efficient powertrain system |
WO2010106560A1 (en) * | 2009-03-19 | 2010-09-23 | Alenia Aeronautica S.P.A. | Starting and electricity generating system for a reciprocating engine |
US8496079B2 (en) | 2009-09-16 | 2013-07-30 | Swissauto Powersport Llc | Electric vehicle and on-board battery charging apparatus therefore |
WO2014002845A1 (en) * | 2012-06-29 | 2014-01-03 | 株式会社マキタ | Power device for portable working machine, and portable working machine |
JP2014009643A (en) * | 2012-06-29 | 2014-01-20 | Makita Corp | Power unit for portable work machine |
US10744868B2 (en) | 2016-06-14 | 2020-08-18 | Polaris Industries Inc. | Hybrid utility vehicle |
US10780770B2 (en) | 2018-10-05 | 2020-09-22 | Polaris Industries Inc. | Hybrid utility vehicle |
US11370266B2 (en) | 2019-05-16 | 2022-06-28 | Polaris Industries Inc. | Hybrid utility vehicle |
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