JPS63266154A - Piston for internal combustion engine - Google Patents
Piston for internal combustion engineInfo
- Publication number
- JPS63266154A JPS63266154A JP8553788A JP8553788A JPS63266154A JP S63266154 A JPS63266154 A JP S63266154A JP 8553788 A JP8553788 A JP 8553788A JP 8553788 A JP8553788 A JP 8553788A JP S63266154 A JPS63266154 A JP S63266154A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- chamber
- valve
- control chamber
- closing member
- 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
- 238000002485 combustion reaction Methods 0.000 title claims description 5
- 230000006835 compression Effects 0.000 claims description 12
- 238000007906 compression Methods 0.000 claims description 12
- 239000007788 liquid Substances 0.000 claims description 2
- 238000010276 construction Methods 0.000 description 1
- 230000008602 contraction Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
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
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/044—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of an adjustable piston length
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は、内燃機関用の圧縮行程の変動可能なぎストン
であって、ぎストンピンに枢着されたピストン内側部分
及びぎストン内側部分にテレスコープ式に移動可能に保
持されたピストンクラウンから成り、かつぎストン内側
部分とピストンクラウンとの間に形成され互いに接続さ
れた第１及び第２の室を有しており、室の容積がピスト
ン内側部分とピストンクラウンとの間の相対運動に際し
互いに逆比的に変えられるようになっており、両方の室
が外部から第１の室（制御室）内に流入しかつ流出する
非圧縮性の液体によって負荷されており、制御室が一方
向流入弁（逆止弁）及び圧力及び回転数に関連して作用
する一方向ｂｊｔ出弁（圧力制限弁）を備えており、制
御室と第２の室（緩衝室）との間に緩衝室の方向へ開く
一方向弁（逆止弁）及び絞り孔が設けられている形式の
ものに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a compression stroke variable giston for an internal combustion engine, which includes a piston inner portion pivotally connected to a piston pin and a piston movably held in a telescopically movable piston inner portion. It has first and second chambers formed between the piston inner part and the piston crown and connected to each other, and the volume of the chamber is the same as that between the piston inner part and the piston crown. both chambers are loaded with an incompressible liquid flowing into and out of the first chamber (control chamber) from the outside; The chamber is equipped with a one-way inlet valve (check valve) and a one-way bjt outlet valve (pressure limiting valve) that acts in relation to pressure and rotational speed, and there is a connection between the control chamber and the second chamber (buffer chamber). It relates to a type in which a one-way valve (check valve) that opens toward the buffer chamber and a throttle hole are provided in between.
前記形式のピストンは、例えば ＤＥ３３４６９６６Ａ１号公報により公知である。Pistons of the above type may be used, for example. It is known from DE3346966A1.
このようなピストンは、燃焼室内の所定の圧力の越えら
れた場合に自由に運動可能なピストンクラウンｉｆスト
ンの圧縮行程を縮小する方向に移動させるように働く。Such a piston serves to reduce the compression stroke of the freely movable piston crown if a predetermined pressure in the combustion chamber is exceeded.
圧縮行程をいつ縮小するかは、制御室に接続された圧力
制限弁を応動させる限界圧によって規定される。ピスト
ンクラウンは各回転に際しピストン行程の」二死点の範
囲で緩に室に作用するピストンクラウンの慣性力に基づ
き圧縮行程を拡大する方向に移動させられる。作業サイ
クル毎の圧縮行程変動は、制御室と緩衝室との間の絞り
孔の横断面の大きさによって規定される圧縮行程拡大と
圧力制限弁、回転数（若しくは圧力制限弁の開放時間）
及び制御室内のオイル圧に関連する圧縮行程縮小との差
異から生じる。When to reduce the compression stroke is determined by a threshold pressure which triggers a pressure limiting valve connected to the control chamber. During each rotation, the piston crown is moved in the direction of enlarging the compression stroke based on the inertial force of the piston crown that acts gently on the chamber in the range of the second dead center of the piston stroke. The compression stroke fluctuation for each work cycle is determined by the expansion of the compression stroke determined by the cross-sectional size of the throttle hole between the control chamber and the buffer chamber, the pressure limiting valve, and the rotation speed (or the opening time of the pressure limiting valve).
and the compression stroke reduction associated with the oil pressure in the control chamber.
所定の点火圧の場合に規定されたバランス状態（すなわ
ち同じ圧縮行程拡大及び縮小）はもちろん所定の回転数
の場合にのみ維持される。The balance condition defined for a given ignition pressure (ie the same compression stroke expansion and contraction) is of course maintained only at a given rotational speed.
回゛転数の増大に伴って圧力制限弁の開放時間が短くな
り、ひいては流過量が少なくなる。その結果バランス状
態が圧縮行程を拡大する方向へ移る。As the rotational speed increases, the opening time of the pressure limiting valve becomes shorter, and thus the flow rate decreases. As a result, the balance state shifts to the direction of expanding the compression stroke.
このような問題は周知で、例えばＵＳ −ＰＳ３１ ＜
Ｓｌ １１２号及びＤｇ３３４６９６６Ａ１号公報に記
載されている。Such problems are well known, for example US-PS31 <
It is described in SI 112 and Dg3346966A1.
問題を解決するために、ＵＳ−ＰＳ公報に記載の圧力制
限弁においては圧力制限弁の開放時間が機関回転数の増
大に伴って長くされる。このような手段は圧力制限弁を
複雑で故障しやすい構造のものにする。To solve this problem, in the pressure limiting valve described in the US-PS publication, the opening time of the pressure limiting valve is lengthened as the engine speed increases. Such measures make pressure limiting valves complex and prone to failure.
ＤＥ３６４６９６６に１号公報に記載の手段においては
、回転数に関連した調整動作が制御室と緩衝室との間に
設けられた絞り孔の横断面を機関回転数の増大に際し回
転数に関連した弁によって小さくすることに基づき行な
われる。In the means described in DE 3646966 No. 1, the adjustment operation related to the rotation speed changes the cross section of the throttle hole provided between the control chamber and the buffer chamber when the engine speed increases. This is done on the basis of reducing the size by
本発明の課題は、ピスト／の回転数の変動と一緒に変化
する調整動作の問題を構造的に簡単に取除くことである
。The object of the invention is to eliminate the problem of adjustment movements that vary with fluctuations in the rotational speed of the piston in a simple construction.
この課題を解決するために本発明の構成では、圧力制限
弁の閉鎖部材がコンロッドの方向に作用するはね力によ
って閉じられており、閉鎖部材の案内路が２ストン軸線
に対して０°よりも太きく９０°よりも小さい範囲の間
で傾斜している。In order to solve this problem, the present invention provides an arrangement in which the closing member of the pressure limiting valve is closed by a spring force acting in the direction of the connecting rod, and the guide path of the closing member is oriented at an angle of 0° with respect to the two-stone axis. It is also thick and tilted within a range smaller than 90°.
閉鎖部材の案内路の傾斜角は通常は１５°と７５°より
も小さい範囲の間である。The angle of inclination of the guideway of the closure member is usually between 15° and less than 75°.
圧力制限弁の閉鎖部材の案内路をピストンの運動方向に
対して傾斜しであることによって、運転時に閉鎖部材に
よって生ぜしめられる慣性力が案内路に対して垂直に作
用する力成分と閉鎖部羽を負荷するばねの方向に作用す
る力成分とに分けられる。ばねの方向に作用する力成分
はピストンの上死点位置でばね力と逆に向いており、そ
の結果圧力制限弁が早期にかつ長く開かれる。これによ
ってぎストンの調整動作が機関回転数の変動に際しても
コンスタントに維持される。By slanting the guide path of the closing member of the pressure limiting valve with respect to the direction of movement of the piston, the inertial force generated by the closing member during operation is combined with a force component acting perpendicularly to the guide path and the closing blade. It can be divided into a force component that acts in the direction of the spring that loads the force. The force component acting in the direction of the spring is directed opposite to the spring force at the top dead center position of the piston, so that the pressure limiting valve opens earlier and longer. This ensures that the adjusting action of the giston remains constant even when the engine speed changes.
次に図面を用いて本発明の実施例を具体的に説明する。Next, embodiments of the present invention will be specifically described using the drawings.
図面に示すように、ピストンのピストンクラウン１はピ
ストンの圧縮行程を変えるために、ピストンであつて、
ピストンピン２に結合されたぎストン内側部分３に対し
て軸線方向に移動可能になっている。As shown in the drawing, the piston crown 1 of the piston is a piston in order to change the compression stroke of the piston.
It is axially movable relative to the piston inner part 3 which is connected to the piston pin 2.
圧縮行程の変動は制御室４及び緩衝室５を満たす若しく
は空にすることによって行なわれる。The compression stroke is varied by filling or emptying the control chamber 4 and the buffer chamber 5.
制御室及び緩衝室の容積は互いに逆比的に変えられる。The volumes of the control chamber and the buffer chamber are varied inversely to each other.
制御室及び緩衝室を制御する圧力オイルはピストンピン
２の内部を通して逆止弁６を介して供給される。緩衝室
５を制御室４に接続するために、制御室４に向かって閉
鎖する逆止弁７並びに絞り孔８が用いられている。制御
室４からは圧力オイルは圧力制限弁９を通って機関クラ
ンク室へ戻される。Pressure oil for controlling the control chamber and the buffer chamber is supplied through the piston pin 2 via the check valve 6. In order to connect the buffer chamber 5 to the control chamber 4, a check valve 7 which closes toward the control chamber 4 as well as a throttle hole 8 are used. From the control chamber 4, pressure oil is returned to the engine crankcase through a pressure limiting valve 9.
圧力制限弁９はピストン軸線に対してほぼ４５度、傾斜
している。圧力制限弁９は中空室１０、中空室１０のピ
ストンクラウンから離れた側の端部に配置された弁座１
１及び、玉として構成され弁座１１にはね１３の押し力
を受けて当接する閉鎖部材１２から成っている。矢印Ｂ
は制御室４から圧力制限弁９への圧力オイルの流出を示
しており、矢印Ｃは圧力制限弁９からの圧力オイルの流
出を示している。The pressure limiting valve 9 is inclined at approximately 45 degrees to the piston axis. The pressure limiting valve 9 includes a hollow chamber 10 and a valve seat 1 disposed at the end of the hollow chamber 10 on the side remote from the piston crown.
1, and a closing member 12 which is configured as a ball and abuts against the valve seat 11 under the pushing force of a spring 13. Arrow B
indicates the outflow of pressure oil from the control chamber 4 to the pressure limiting valve 9, and arrow C indicates the outflow of pressure oil from the pressure limiting valve 9.
閉鎖部材１２のざストン上死点で作用する慣性力には、
中空室１００案内路として役立つ壁に閉鎖部材１２の接
することに基づき力成分ＮとＦとに分けられる。力成分
Ｎは閉鎖部材の閉鎖力に影響を及はさないのに対して、
力成分Ｆはば柾１３り押し力と逆の方向に向いている。The inertial force that acts on the closing member 12 at the top dead center is:
The cavity 100 is divided into force components N and F due to the contact of the closing member 12 with the wall which serves as a guideway. Whereas the force component N has no influence on the closing force of the closure member,
The force component F is directed in the opposite direction to the pushing force.
従って、傾斜角、の選択によって、機関回転数の増大に
際しはね■３の押し力に対する逆作用をどの程度生せし
めるかが規定される。この場合、逆作用はピストンの上
死点範囲での滞在時間が機関回転数の増大に際し短くな
るにもかかわらず、ぎストンの調整動作が回転数範囲全
体にわたってほぼ一様になるように設定されねばならな
い。このために、圧力制限弁の正確な傾斜角をそれぞれ
シミュレーションの運転データを用いて実験的に若しく
は計算的に求める必要がある。Therefore, the selection of the angle of inclination determines the degree to which the pushing force of the spring 3 is counteracted when the engine speed increases. In this case, the reverse effect is set in such a way that the adjusting action of the piston is approximately uniform over the entire speed range, although the piston dwell time in the top dead center range becomes shorter with increasing engine speed. Must be. For this purpose, it is necessary to determine the exact inclination angle of the pressure limiting valve experimentally or computationally using simulation operating data.
図面は本発明の実施例の縦断面図である。 The drawing is a longitudinal sectional view of an embodiment of the invention.
Claims (1)
て、ピストンピンに枢着されたピストン内側部分（３）
及びピストン内側部分にテレスコープ式に移動可能に保
持されたピストンクラウン（１）から成り、かつピスト
ン内側部分とピストンクラウンとの間に形成され互いに
接続された第１及び第２の室（４、５）を有しており、
室の容積がピストン内側部分（３）とピストンクラウン
（１）との間の相対運動に際し互いに逆比的に変えられ
るようになつており、両方の室が外部から第１の室（制
御室４）内に流入しかつ流出する非圧縮性の液体によつ
て負荷されており、制御室（４）が一方向流入弁（逆止
弁６）及び圧力及び回転数に関連して作用する一方向流
出弁（圧力制限弁９）を備えており、制御室と第２の室
（緩衝室５）との間に緩衝室（５）の方向へ開く一方向
弁（逆止弁７）及び絞り孔（８）が設けられている形式
のものにおいて、圧力制限弁（９）の閉鎖部材（１２）
がコンロツドの方向に作用するばね力によつて閉じられ
ており、閉鎖部材（１２）の案内路がピストン軸線に対
して０°よりも大きく ９０°よりも小さい範囲の間で傾斜していることを特徴
とする内燃機関用のピストン。 ２、閉鎖部材（１２）の案内路がピストン軸線に対して
少なくとも１５°と７５°よりも小さい範囲の間で傾斜
している請求項１記載のピストン。[Claims] 1. A piston with a variable compression stroke for an internal combustion engine, the inner piston portion (3) being pivotally connected to a piston pin.
and a piston crown (1) telescopically movably held on the piston inner part, and first and second chambers (4, 5),
The volumes of the chambers are adapted to be changed inversely to each other during relative movement between the piston inner part (3) and the piston crown (1), and both chambers are connected from the outside to the first chamber (control chamber 4). ) is loaded by an incompressible liquid flowing into and out of the control chamber (4), and the control chamber (4) has a one-way inlet valve (check valve 6) and a one-way acting in conjunction with the pressure and speed. It is equipped with an outflow valve (pressure limiting valve 9), and a one-way valve (check valve 7) that opens toward the buffer chamber (5) and a throttle hole between the control chamber and the second chamber (buffer chamber 5). (8), the closing member (12) of the pressure limiting valve (9)
is closed by a spring force acting in the direction of the connecting rod, and the guide path of the closing member (12) is inclined with respect to the piston axis between a range greater than 0° and less than 90°. A piston for internal combustion engines featuring: 2. Piston according to claim 1, characterized in that the guideway of the closing member (12) is inclined with respect to the piston axis between at least 15[deg.] and less than 75[deg.].
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19873712842 DE3712842C1 (en) | 1987-04-15 | 1987-04-15 | Plunger with variable compression height for internal combustion engines |
| DE3712842.6 | 1987-04-15 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS63266154A true JPS63266154A (en) | 1988-11-02 |
Family
ID=6325716
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8553788A Pending JPS63266154A (en) | 1987-04-15 | 1988-04-08 | Piston for internal combustion engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS63266154A (en) |
| DE (1) | DE3712842C1 (en) |
| GB (1) | GB2203817A (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2223292B (en) * | 1988-09-29 | 1992-04-15 | T & N Technology Ltd | Improvements in and relating to pistons |
| US5247911A (en) * | 1991-10-23 | 1993-09-28 | Vratislav Nenicka | Compression ratio control in gasoline engines |
| DE69817344T2 (en) * | 1998-09-09 | 2004-06-09 | Morse Tec Europe S.R.L. | Drive chain or belt tensioning device with a piston with a plurality of parts which can be moved relative to one another |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3405697A (en) * | 1967-12-08 | 1968-10-15 | Continental Aviat & Eng Corp | Hollow valve construction for variable compression ratio piston |
| DE3346966A1 (en) * | 1983-12-24 | 1985-07-04 | Mahle Gmbh, 7000 Stuttgart | Trunk piston with variable compression level for combustion engines |
-
1987
- 1987-04-15 DE DE19873712842 patent/DE3712842C1/en not_active Expired
-
1988
- 1988-04-07 GB GB08808073A patent/GB2203817A/en not_active Withdrawn
- 1988-04-08 JP JP8553788A patent/JPS63266154A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE3712842C1 (en) | 1988-10-27 |
| GB8808073D0 (en) | 1988-05-11 |
| GB2203817A (en) | 1988-10-26 |
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