JPS6111410A - Valve device of opening and closing mechanism in prime mover - Google Patents
Valve device of opening and closing mechanism in prime moverInfo
- Publication number
- JPS6111410A JPS6111410A JP59130639A JP13063984A JPS6111410A JP S6111410 A JPS6111410 A JP S6111410A JP 59130639 A JP59130639 A JP 59130639A JP 13063984 A JP13063984 A JP 13063984A JP S6111410 A JPS6111410 A JP S6111410A
- Authority
- JP
- Japan
- Prior art keywords
- cylinder
- valve
- oil
- piston
- opening
- 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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
- F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
- F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
- F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は原動機の弁開閉機構装置に関し、更に詳細には
、ピストン駆動部材によってシリンダー内を摺動するピ
ストンと、そのシリンダー側面にシリンダー内の油の排
出量を調節出来る孔と、更に上述したシリンダーと連通
ずる油圧発生部分とから構成された弁開閉機構装置に関
する。この種のレシプロ式原動機においては、高出力を
得る為の方法として、吸入弁及び排気弁の弁開閉時期を
早く開いて遅く閉じ、又弁のリフト量については、その
リフト量を大きくし、更に各弁の弁径を大きくする事に
よって高出力を確保していた。よって低速回転時におい
ては吸入行程時の吸気流速が遅くなりシリンダー内に渦
流が発生しにくい性質があった。そのためアイドリング
や低速回転時に燃焼が不安定となり、その結果低速回転
でのトルクが小さくなってしまう欠点があった。この欠
点を克服する為原動機の回転によって各弁の弁開閉時期
及び弁リフト量を可変する弁開閉機構装置が本願出願人
と同一の出願人による特願58−204272号に於い
て提案された。この提案は第1図の概略断面説明図の様
にピストン駆動部材によってシリンダー内を摺動するピ
ストンと、そのシリンダー側面にシリンダー内の油の排
出量を調整出来る孔と、更に上述したシリンダーと連通
ずる油圧発生部分とから構成されており、この同装置中
の主排出油調整弁15を開の位置と閉の位置の2段階に
切り替える事によって、シリンダー内に残った油に弁バ
ネの反発力に勝る油圧が発生する時期を変えた。よって
、吸入弁及び排気弁の弁開閉時期及び弁リフト量は低速
回転時と高速回転時によって変わり、低速回転高トルク
型と高速回転高出力型の両特性をカバーした弁開閉機構
装置として所期の目的は達成された。しかし、中速回転
域に適した弁開閉時期及びリフト量は得られなかった。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a valve opening/closing mechanism device for a prime mover, and more specifically, a piston that slides in a cylinder by a piston driving member, and a side surface of the cylinder that can adjust the amount of oil discharged from the cylinder. The present invention relates to a valve opening/closing mechanism device comprising a hole and a hydraulic pressure generating portion communicating with the above-mentioned cylinder. In this type of reciprocating prime mover, in order to obtain high output, the valve opening/closing timing of the intake valve and exhaust valve is opened early and closed late, and the lift amount of the valve is increased. High output was ensured by increasing the diameter of each valve. Therefore, during low-speed rotation, the intake flow rate during the intake stroke becomes slow, making it difficult for swirls to occur within the cylinder. As a result, combustion becomes unstable during idling or low-speed rotation, resulting in a drawback that torque at low-speed rotation becomes small. In order to overcome this drawback, a valve opening/closing mechanism device was proposed in Japanese Patent Application No. 58-204272 by the same applicant as the present applicant, in which the valve opening/closing timing and valve lift amount of each valve are varied by the rotation of the prime mover. This proposal consists of a piston that slides inside the cylinder by a piston drive member, as shown in the schematic cross-sectional diagram in Figure 1, a hole on the side of the cylinder that can adjust the amount of oil discharged from the cylinder, and a hole connected to the cylinder described above. By switching the main discharge oil regulating valve 15 in this device between the open and closed positions, the repulsive force of the valve spring is applied to the oil remaining in the cylinder. The timing at which hydraulic pressure is generated has been changed. Therefore, the valve opening/closing timing and valve lift amount of the intake valve and exhaust valve change depending on low speed rotation and high speed rotation, and the valve opening/closing mechanism device that covers both the characteristics of low speed rotation high torque type and high speed rotation high output type is designed as a valve opening/closing mechanism device. objective was achieved. However, the valve opening/closing timing and lift amount suitable for the medium speed rotation range could not be obtained.
本発明は上述した問題に鑑みてなされたもので、その目
的は先に提案された弁開閉機構装置の主排出油調整弁1
5を開の位置から閉の位置まで無段階又は段階的に可変
する事によって各回転時に適した弁開閉時期及び弁リフ
ト量を確保し、更に高速回転時にピストン駆動部材によ
ってピストンが反復駆動され続け、シリンダー内の油が
発熱し膨張した量だけシリンダー外へ排出させる時の通
路を設ける事によってピストン駆動部材がピストンを駆
動していない時、吸入弁又は排気弁を押し開けない様に
した弁開閉機構装置の提供にある。以下図面を用いてこ
の発明の好ましい実施例を詳細に説明する。第1図及び
第2図において3はピストン駆動部材でこの実施例の場
合はカムを用いている。4はピストン駆動部材3によっ
て駆動されたピストンで、受けた駆動力をシリンダー5
内の油に加え油圧を発生させる。5はシリンダーで側面
にシリンダー内の油の排出量を調節出来る孔が2個ある
。14は吸入弁。15はシリンダー側面に位置する主排
出油調整弁で低速回転時の全開の位置から高速回転時の
全開の位置まで無段階又は段階的に可変移動しその開口
面積を可変する事によってシリンダー内の油の排出量を
無段階又は段階的に可変する。16は副排出油調整弁で
多気筒型原動機において燃費を節約する為可変気筒とす
る場合に開となってシリンダー内の油を排出し、ピスト
ン駆動部材3によってピストン4が駆動されても吸入弁
、排気弁を押し開けない様にする。又、上述した主排出
油調整弁15と副排出油調整弁16は例えば気化器のス
ロットル弁と連動しく図示せず)更に水温、吸入管負圧
量、車速、シフト位置口し、他端部がシリンダー5外に
開口する。更にシリンダー5内における開口位置はピス
トン駆動部材3がピストン4を駆動しない時開口し、ピ
ストン4を駆動した初期段階にピストン4によって閉じ
られる位置とし、単数又は複数の設置が考えられる。又
この連通路はシリンダー5とピストン4間の潤滑作用が
ある。他の連通路位置としては第4図の様な方法も考え
られる。The present invention has been made in view of the above-mentioned problems, and its purpose is to improve the main discharge oil regulating valve 1 of the valve opening/closing mechanism device proposed previously.
By variable steplessly or stepwise from the open position to the closed position, the valve opening/closing timing and valve lift amount suitable for each rotation can be secured, and the piston can be repeatedly driven by the piston driving member during high speed rotation. A valve opening/closing method that prevents the intake valve or exhaust valve from being pushed open when the piston drive member is not driving the piston by providing a passage for discharging the amount of oil in the cylinder that heats up and expands to the outside of the cylinder. The purpose is to provide mechanical devices. Preferred embodiments of the present invention will be described in detail below with reference to the drawings. In FIGS. 1 and 2, reference numeral 3 denotes a piston driving member, and in this embodiment, a cam is used. 4 is a piston driven by the piston driving member 3, and the received driving force is transferred to the cylinder 5.
Generates hydraulic pressure in addition to the oil inside. 5 is a cylinder with two holes on the side that can adjust the amount of oil discharged from the cylinder. 14 is a suction valve. Reference numeral 15 is a main discharge oil regulating valve located on the side of the cylinder, which moves steplessly or stepwise from a fully open position at low speed rotation to a fully open position at high speed rotation, and controls the oil in the cylinder by varying its opening area. Variable emission amount steplessly or stepwise. Reference numeral 16 denotes a sub-discharge oil regulating valve, which is opened when variable cylinders are used to save fuel consumption in a multi-cylinder type prime mover and discharges oil in the cylinder. , be careful not to push the exhaust valve open. In addition, the above-mentioned main discharge oil regulating valve 15 and sub-discharge oil regulating valve 16 are connected to, for example, the throttle valve of the carburetor and are not shown). opens outside the cylinder 5. Further, the opening position in the cylinder 5 is such that it is opened when the piston drive member 3 does not drive the piston 4, and is closed by the piston 4 in the initial stage of driving the piston 4, and it is possible to install one or more openings. Further, this communication passage has a lubricating effect between the cylinder 5 and the piston 4. As for other communication path positions, a method as shown in FIG. 4 can also be considered.
35及び36は1シリンダー当り吸入弁2本とした場合
の各吸入弁である(第5図)。更に第5図における3−
1,3−2はピストン駆動部材のカムで3−1は低速回
転から中速回転域までを受は持つ為のカムプロフィルに
設定され、3−2は中速回転域から高速回転域までを受
は持つ為のカムプロフィルに設定されている。37は副
排出油調整弁16−2に開口した孔である。Reference numerals 35 and 36 indicate intake valves when there are two intake valves per cylinder (Fig. 5). Furthermore, 3- in Figure 5
1 and 3-2 are the cams of the piston driving member, 3-1 is set to a cam profile that supports from low speed rotation to medium speed rotation range, and 3-2 is set to have a cam profile from medium speed rotation range to high speed rotation range. The receiver is set to a cam profile for holding. 37 is a hole opened to the sub-discharge oil regulating valve 16-2.
以上の構成により本発明に係る弁開閉機構装置の作動に
ついて説明する。The operation of the valve opening/closing mechanism device according to the present invention with the above configuration will be explained.
第1図及び第2図は先願出願時における弁開閉機構装置
の概略断面説明図であるが、本発明は主排出油調整弁1
5の位置を第2図の低速回転時における全開の位置から
第1図の高速回転時における全開の位置まで原動機の回
転数に応じて無段階又は段階的に可変させる事によって
主排出油調整弁15の孔の開口面積を可変させ、ピスト
ン駆動部材3がピストン4を駆動した時シリンダー5内
からシリンダー5外へ排出する油量を原動機の回転数に
応じて無段階又は段階的に可変出来、よってピストン駆
動部材3がピストン4を駆動し、吸入弁、排気弁の各弁
バネに勝る油圧がシリンダー5内の油に発生する時期を
原動機の回転数によって可変する事が出来るものである
。ゆえに吸入弁、及び排気弁の弁開閉時期及び弁リフト
量を原動機の回転数によって可変する事が出来、結果原
動機のトルク、出力、燃費の向上という本来の目的を有
効に達成できるものである。又、上述した実施例は主排
出油調整弁15を高速回転時において全閉としたが、こ
れに限らず全閉前で止め、ピストン駆動部材3がピスト
ン4を反復駆動してシリンダー5内の油が発熱し膨張し
た時、全閉前の主排出油調整弁15の開口部よりその膨
張した量だけシリンダー5外へ排出する事によって、ピ
ストン駆動部材3がピストン4を駆動していない時に膨
張したシリンダー5内の油で吸入弁、排気弁を押し開け
る事を防止出来る。1 and 2 are schematic cross-sectional explanatory views of the valve opening/closing mechanism device at the time of filing of the earlier application, but the present invention is based on the main discharge oil regulating valve 1.
The main discharge oil regulating valve can be adjusted stepwise or stepwise by varying the position of 5 from the fully open position at low speed rotation shown in Figure 2 to the fully open position at high speed rotation shown in Figure 1, depending on the rotational speed of the prime mover. By varying the opening area of the hole 15, the amount of oil discharged from the inside of the cylinder 5 to the outside of the cylinder 5 when the piston driving member 3 drives the piston 4 can be varied steplessly or stepwise according to the rotational speed of the prime mover. Therefore, the piston driving member 3 drives the piston 4, and the timing at which hydraulic pressure is generated in the oil in the cylinder 5, which exceeds the valve springs of the intake valve and the exhaust valve, can be varied depending on the rotational speed of the prime mover. Therefore, the valve opening/closing timing and valve lift amount of the intake valve and exhaust valve can be varied depending on the rotation speed of the prime mover, and as a result, the original purpose of improving the torque, output, and fuel efficiency of the prime mover can be effectively achieved. Further, in the above-described embodiment, the main discharge oil regulating valve 15 is fully closed during high-speed rotation, but the invention is not limited to this, and the piston driving member 3 repeatedly drives the piston 4 to stop the valve before fully closing. When the oil heats up and expands, by discharging the expanded amount out of the cylinder 5 through the opening of the main discharge oil regulating valve 15 before it is fully closed, the oil expands when the piston driving member 3 is not driving the piston 4. This prevents the oil in the cylinder 5 from pushing open the intake valve and exhaust valve.
又、膨張したシリンダー5内の油が吸入弁、排気弁を押
し開ける事を防止する他の方法として第3図の様に、シ
リンダー5内に一端部が開口し、他端部がシリンダー5
外に開口した単数又は複数の連通路34を設ける事によ
ってこの連通路よりピストン駆動部材3がピストン4を
駆動していない時膨張した油をシリンダー5外へ排出す
れば上述した主排出油調整弁15を全開前で止める方法
と同様に膨張したシリンダー5内の油によって吸入弁、
排気弁を押し開ける事を防止する事が出来るものである
。Another method for preventing the expanded oil in the cylinder 5 from pushing open the intake valve and exhaust valve is to open one end of the cylinder 5 into the cylinder 5 and open the other end of the cylinder 5, as shown in FIG.
By providing one or more communication passages 34 that are open to the outside, the expanded oil can be discharged from the communication passages to the outside of the cylinder 5 when the piston drive member 3 is not driving the piston 4, and the above-mentioned main discharge oil regulating valve can be used. Similar to the method of stopping cylinder 15 before it is fully opened, the oil in expanded cylinder 5 causes the suction valve to
This prevents the exhaust valve from being pushed open.
以上の様に本発明はシリンダー内の油の排出量を調整す
る主排出油調整弁を無段階又は段階的に可変する事によ
って吸入弁、排気弁の弁開閉時期及びリフト量を可変出
来、その結果低速回転時に−7=
おける高トルクから高速回転における高出力まで無段階
又は段階的に可変する事ができる。また、本発明によれ
ば、シリンダー内の油の発熱による油の膨張を単数又は
複数の連通路によってシリンダー外へ排出する事によっ
て吸入弁、排気弁を押し開ける事を防止できるものであ
る。As described above, the present invention makes it possible to vary the valve opening/closing timing and lift amount of the intake valve and exhaust valve by varying the main discharge oil regulating valve, which regulates the discharge amount of oil in the cylinder, either steplessly or stepwise. As a result, it is possible to vary the torque steplessly or stepwise from a high torque of -7 at low speed rotation to a high output at high speed rotation. Further, according to the present invention, by discharging the expansion of oil due to heat generated by the oil in the cylinder to the outside of the cylinder through one or more communicating passages, it is possible to prevent the intake valve and the exhaust valve from being forced open.
なお上述した実施例においては1シリンダー当り吸入弁
1本の場合において詳述したが、この実施例に限るもの
ではなく、たとえば1シリンダー当り吸入弁2本の原動
機の場合においては2本の吸入弁35.36に上述した
弁開閉機構装置を備えること(第5図)によって主排出
油調整弁15−1.15=2及び副排出油調整弁1B−
1゜16−2の開閉を種々組み合わせを行なう事によっ
て第6図から第8図の様な各種弁開閉時期を得る事が出
来る。例えば第6図における弁開閉時期は第1吸入弁3
5側がアイドリングから中速回転域までに適した弁の開
閉を行なう。この時第2吸入弁36側の副排出油調整弁
16−2が開となってピストン駆動部材3−2によって
シリンダー5=8−
一2内のピストン4−2が駆動され続けても副排出油調
整弁16−2に開口した孔37よりシリンダー5−2内
の油をシリンダー5−2外へ排出する事によって第2吸
入弁36は閉の状態を保ち続ける事になる。よってアイ
ドリング時から低速回転時までにおいては主排出油調整
弁15−1も開らいている為、シリンダー5−1内の油
は多く排出されその結果第1吸入弁35の弁開閉時期は
遅゛く開いて早めに閉じる為燃焼室内への吸気流速は早
まり充分渦流が発生し、燃焼室内は安定した速やかな燃
焼が行なわれ高いトルクを確保することができる。更に
回転が上昇するにしたがって主排出油調整弁15−1を
無段階又は段階的に可変する事によって中速回転域まで
各弁の開閉時期は無段階又は段階的に可変し、それは除
々に弁開閉時期が早く開いて遅く閉じ始め、又、弁リフ
ト量も大きくなっていく。次に原動機が中速回転域に達
する頃に第2吸入弁36側の副排出油調整弁16−2が
閉となってシリンダー5−2内の油の排出を止め、よっ
て第2吸入弁36が開閉を始める。Although the above-mentioned embodiment has been described in detail for the case where there is one suction valve per cylinder, the invention is not limited to this example. For example, in the case of a prime mover with two suction valves per cylinder, two suction valves may be used. By providing the above-mentioned valve opening/closing mechanism device in 35.36 (Fig. 5), the main discharge oil regulating valve 15-1.15=2 and the sub-discharge oil regulating valve 1B-
By performing various combinations of opening and closing of 1°16-2, various valve opening and closing timings as shown in FIGS. 6 to 8 can be obtained. For example, the valve opening/closing timing in FIG.
The 5 side opens and closes the valve suitable for the range from idling to medium speed rotation. At this time, even if the sub-discharge oil regulating valve 16-2 on the second suction valve 36 side is opened and the piston 4-2 in the cylinder 5=8-12 continues to be driven by the piston driving member 3-2, the sub-discharge oil is discharged. By discharging the oil in the cylinder 5-2 to the outside of the cylinder 5-2 through the hole 37 opened in the oil regulating valve 16-2, the second suction valve 36 continues to remain closed. Therefore, since the main discharge oil regulating valve 15-1 is also open from idling to low speed rotation, a large amount of oil in the cylinder 5-1 is discharged, and as a result, the valve opening/closing timing of the first intake valve 35 is delayed. Since it opens wide and closes early, the intake air flow speed into the combustion chamber increases and a sufficient vortex is generated, ensuring stable and rapid combustion within the combustion chamber and ensuring high torque. Furthermore, as the rotation increases, the main discharge oil regulating valve 15-1 is varied steplessly or stepwise, so that the opening/closing timing of each valve can be varied steplessly or stepwise up to the medium speed rotation range. The opening/closing timing starts to open early and close late, and the valve lift also increases. Next, when the prime mover reaches a medium speed rotation range, the sub-discharge oil regulating valve 16-2 on the second suction valve 36 side closes and stops discharging the oil in the cylinder 5-2. begins to open and close.
この第2吸入弁36側のピストン駆動部材3−2は高速
用に設定されたカムプロフィルを有している為、第1吸
入弁35側の主排出油調整弁15−1が全閉となって第
1吸入弁35を開閉する時の弁開閉時期よりも第2吸入
弁36側の弁開閉時期は早く開いて遅く閉じる。よって
2本の吸入弁35.36の開閉時期に差を与える事で燃
焼室内には渦流が発生する。ゆえに燃焼は速やかに行な
われ高出力を確保する事が出来る。次に更に原動機が高
回転になるにしたがい主排出油調整弁15−2も無段階
又は段階的に閉じて開口面積をせばめ、弁開閉時期は更
に早く開いて遅く閉じ、又、弁リフト量もさらに大きく
なって高回転時に必要な混合気を充分燃焼室内へ供給出
来る。この結果燃焼室内へ充分吸入した混合気と、更に
渦流の効果によって速やかに燃焼が行なわれ高回転高出
力を得る事が出来る。又、排気弁側については説明を省
いたが吸入弁側と同様な弁開閉機構装置を設ける事によ
って、低速回転時の弁開閉時期は遅く開いて早めに閉じ
る事によって吹き抜けを防止し、高速回転時においては
早く開いて遅く閉じる事によって吸入弁側とのオーバー
ラツプ量を大きくし吸排気効率の向上を計ることが出来
るものである。Since the piston drive member 3-2 on the second suction valve 36 side has a cam profile set for high speed, the main discharge oil regulating valve 15-1 on the first suction valve 35 side is fully closed. The valve opening/closing timing of the second suction valve 36 opens earlier and closes later than the valve opening/closing timing when the first suction valve 35 is opened and closed. Therefore, by providing a difference in the timing of opening and closing of the two intake valves 35 and 36, a vortex is generated within the combustion chamber. Therefore, combustion occurs quickly and high output can be ensured. Next, as the engine speeds up further, the main discharge oil regulating valve 15-2 also closes steplessly or in stages to narrow the opening area, and the valve opening/closing timing opens earlier and closes later, and the amount of valve lift also decreases. It becomes even larger and can supply the necessary air-fuel mixture into the combustion chamber at high speeds. As a result, due to the air-fuel mixture sufficiently drawn into the combustion chamber and the effect of the vortex, combustion occurs quickly and high rotation and high output can be obtained. Also, although I have omitted the explanation for the exhaust valve side, by providing a valve opening/closing mechanism similar to the intake valve side, the valve opening/closing timing during low speed rotation is opened late and closed early to prevent blow-through, and to prevent blow-through during high speed rotation. In some cases, by opening early and closing late, it is possible to increase the amount of overlap with the intake valve side and improve intake and exhaust efficiency.
なお、上述した実施例において第2吸入弁36の弁開閉
開始時の弁開閉時期は第1吸入弁35のそれより早く開
いて遅く閉じる様に設定したがこれに限らず、第7図の
様に開閉時期を同一にする方法や、第8図の様に始めは
遅く開いて早く閉じ、ある回転数以上に達すると第1吸
入弁35より早く開いて遅く閉じる様な弁開閉時期とす
る方法も考えられる。In the above-described embodiment, the valve opening/closing timing of the second suction valve 36 at the start of opening/closing is set to open earlier and close later than that of the first suction valve 35, but the timing is not limited to this, and as shown in FIG. A method of opening and closing the valve at the same timing, or a method of opening and closing the valve so that it opens late at first and closes early, as shown in Fig. 8, and when it reaches a certain number of revolutions, it opens earlier and closes later than the first intake valve 35. can also be considered.
その他、本発明の技術範囲を逸脱する事なく種々の変更
を加えた実施態様のものも本発明に属するものである。In addition, embodiments in which various changes have been made without departing from the technical scope of the present invention also belong to the present invention.
第1図は先願出願時の弁開閉機構装置における高速回転
時の概略断面説明図。第2図は低速回転時の概略断面説
明図。第3図はシリンダー側面に連通路を設けた概略断
面説明図。第4図は第3図と違った位置に連通路を通し
た方法の概略断面説開園。第5図は1シリンダー当り吸
入弁を2本備えた弁開閉機構装置の吸入弁側の概略断面
説明図。
第6図から第8図は原動機の回転数に対する弁の開閉時
期を示したグラフである。又、第6図から第8図におけ
る斜線部分は2本の吸入弁の開閉時期の差によって生じ
る渦流の量を示す。
3・・・カム(3−1,3−2も含む)4・・・ピスト
ン(4−1,4−2も含む)5・・・シリンダー(15
−1、15−2も含む)14・・・吸入弁
15・・・主排出油調整弁(15−1,15−2も含む
)
16・・・副排出油調整弁(1G−1,16−2も含む
)
17・・・弁バネ
34・・・連通路
35・・・第1吸入弁
36・・・第2吸入弁FIG. 1 is a schematic cross-sectional explanatory diagram of the valve opening/closing mechanism device at high speed rotation when the earlier application was filed. FIG. 2 is a schematic cross-sectional explanatory diagram during low speed rotation. FIG. 3 is a schematic cross-sectional view showing a communication passage provided on the side surface of the cylinder. Figure 4 is a schematic cross-sectional view of the method of opening the park by passing a communication path in a different position than Figure 3. FIG. 5 is a schematic cross-sectional view of the suction valve side of a valve opening/closing mechanism device having two suction valves per cylinder. 6 to 8 are graphs showing the opening/closing timing of the valves relative to the rotational speed of the prime mover. Further, the shaded areas in FIGS. 6 to 8 indicate the amount of vortex generated by the difference in opening and closing timing of the two suction valves. 3...Cam (including 3-1, 3-2) 4...Piston (including 4-1, 4-2) 5...Cylinder (15
-1, 15-2 included) 14... Suction valve 15... Main discharge oil regulating valve (15-1, 15-2 also included) 16... Sub-discharge oil regulating valve (1G-1, 16 -2 included) 17... Valve spring 34... Communication path 35... First suction valve 36... Second suction valve
Claims (4)
るピストンと、そのシリンダー側面にシリンダー内の油
の排出量を調節出来る孔と、更に上述したシリンダーと
連通する油圧発生部分とから構成された弁開閉機構装置
において、前記シリンダー内の油の排出量を調節出来る
主排出油調整弁を原動機の回転数に応じて全開の位置か
ら全閉の位置まで無段階又は段階的に可変する事を特徴
とした弁開閉機構装置。(1) It consists of a piston that slides inside the cylinder by a piston drive member, a hole on the side of the cylinder that can adjust the amount of oil discharged from the cylinder, and a hydraulic pressure generating part that communicates with the cylinder described above. The valve opening/closing mechanism device is characterized in that the main discharge oil regulating valve that can adjust the amount of oil discharged from the cylinder is variable steplessly or stepwise from a fully open position to a fully closed position according to the rotational speed of the prime mover. Valve opening/closing mechanism device.
ンダー内の油の一部をシリンダー外へ排出できる構造と
した特許請求の範囲第1項記載の弁開閉機構装置。(2) The valve opening/closing mechanism device according to claim 1, wherein the main discharge oil regulating valve is structured to be able to stop a portion of the oil in the cylinder before it is fully closed during high-speed rotation and discharge a portion of the oil to the outside of the cylinder.
るピストンと、そのシリンダー側面にシリンダー内の油
の排出量を調節出来る孔と、更に上述したシリンダーと
連通する油圧発生部分とから構成された弁開閉機構装置
において、前記シリンダーに端部が開口し、他端部がシ
リンダー外に開口した単数又は複数の連通路を設け、そ
の連通路のシリンダー内における開口位置をピストン駆
動部材がピストンを駆動しない時開口し、ピストンを駆
動した初期段階にピストンによつて閉じられる位置に設
け、高速回転時に多少のシリンダー内の油の排出ができ
る構造とした事を特徴とする弁開閉機構装置。(3) It consists of a piston that slides inside the cylinder by a piston drive member, a hole on the side of the cylinder that can adjust the amount of oil discharged from the cylinder, and a hydraulic pressure generating part that communicates with the cylinder described above. In the valve opening/closing mechanism device, one or more communicating passages are provided in the cylinder with one end opening and the other end opening outside the cylinder, and a piston driving member drives the piston to change the opening position of the communicating passage in the cylinder. A valve opening/closing mechanism device characterized in that it is opened when the piston is not in use and is closed by the piston in the initial stage of driving the piston, so that a certain amount of oil in the cylinder can be discharged during high speed rotation.
を特徴とする弁開閉機構装置。(4) A valve opening/closing mechanism device characterized by a combination of claims 1 and 3.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59130639A JPS6111410A (en) | 1984-06-25 | 1984-06-25 | Valve device of opening and closing mechanism in prime mover |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59130639A JPS6111410A (en) | 1984-06-25 | 1984-06-25 | Valve device of opening and closing mechanism in prime mover |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS6111410A true JPS6111410A (en) | 1986-01-18 |
Family
ID=15039064
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP59130639A Pending JPS6111410A (en) | 1984-06-25 | 1984-06-25 | Valve device of opening and closing mechanism in prime mover |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS6111410A (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61155608A (en) * | 1984-12-27 | 1986-07-15 | Toyota Motor Corp | Variable valve timing and lifting device |
WO1990014505A1 (en) * | 1989-05-25 | 1990-11-29 | William Bulens | Device for automobile motor timing system with variable valve lifts |
JPH0337313A (en) * | 1989-06-30 | 1991-02-18 | Isuzu Motors Ltd | Variable valve timing lift device |
FR2676501A1 (en) * | 1991-05-15 | 1992-11-20 | Peugeot | Device for actuating a valve in order to vary its lift and/or timing |
-
1984
- 1984-06-25 JP JP59130639A patent/JPS6111410A/en active Pending
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61155608A (en) * | 1984-12-27 | 1986-07-15 | Toyota Motor Corp | Variable valve timing and lifting device |
WO1990014505A1 (en) * | 1989-05-25 | 1990-11-29 | William Bulens | Device for automobile motor timing system with variable valve lifts |
JPH0337313A (en) * | 1989-06-30 | 1991-02-18 | Isuzu Motors Ltd | Variable valve timing lift device |
FR2676501A1 (en) * | 1991-05-15 | 1992-11-20 | Peugeot | Device for actuating a valve in order to vary its lift and/or timing |
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