JP3357519B2 - Diesel engine direct injection combustion chamber - Google Patents

Diesel engine direct injection combustion chamber

Info

Publication number
JP3357519B2
JP3357519B2 JP31993695A JP31993695A JP3357519B2 JP 3357519 B2 JP3357519 B2 JP 3357519B2 JP 31993695 A JP31993695 A JP 31993695A JP 31993695 A JP31993695 A JP 31993695A JP 3357519 B2 JP3357519 B2 JP 3357519B2
Authority
JP
Japan
Prior art keywords
cavity
radiation
virtual line
center axis
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.)
Expired - Fee Related
Application number
JP31993695A
Other languages
Japanese (ja)
Other versions
JPH09158734A (en
Inventor
勝定 築地
節男 山田
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Kubota Corp
Original Assignee
Kubota Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Kubota Corp filed Critical Kubota Corp
Priority to JP31993695A priority Critical patent/JP3357519B2/en
Priority to CN96114585A priority patent/CN1086443C/en
Publication of JPH09158734A publication Critical patent/JPH09158734A/en
Application granted granted Critical
Publication of JP3357519B2 publication Critical patent/JP3357519B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0672—Omega-piston bowl, i.e. the combustion space having a central projection pointing towards the cylinder head and the surrounding wall being inclined towards the cylinder center axis
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0645—Details related to the fuel injector or the fuel spray
    • F02B23/0669—Details related to the fuel injector or the fuel spray having multiple fuel spray jets per injector nozzle
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本発明は、ディーゼルエンジ
ンの直接噴射式燃焼室に関し、詳しくは、燃焼効率を高
めることができるものに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a direct injection combustion chamber of a diesel engine, and more particularly to a combustion chamber capable of improving combustion efficiency.

【０００２】[0002]

【従来の技術】ディーゼルエンジンの直接噴射式燃焼室
の従来技術として図４に示すものがある。これは、本発
明と同様、次のような基本構造を備えている。すなわ
ち、シリンダヘッド１０１に燃料噴射ノズル１０２とス
ワールポート１０３とを設け、ピストンヘッド頂面１０
４に、スキッシュ面１０５を残してバルブリセス１０６
と燃焼用のキャビティ１０７とを凹設し、キャビティ１
０７内に燃料噴射ノズル１０２から燃料１０８を噴射す
るようにし、キャビティ１０７をピストンヘッド頂面１
０４の中央部に、バルブリセス１０６をピストンヘッド
頂面１０４の周縁寄りにそれぞれ配置するとともに、キ
ャビティ１０７とバルブリセス１０６とを相互に連通さ
せて、スワール流１２３がバルブリセス内周面１１２の
案内でキャビティ１０７に導入されるようにしてある。2. Description of the Related Art FIG. 4 shows a prior art of a direct injection combustion chamber of a diesel engine. This has the following basic structure as in the present invention. That is, the fuel injection nozzle 102 and the swirl port 103 are provided on the cylinder head 101, and the piston head top surface 10
4, leaving a squish surface 105 and a valve recess 106
And the cavity 107 for combustion are recessed, and the cavity 1
07, the fuel 108 is injected from the fuel injection nozzle 102, and the cavity 107 is formed in the piston head top surface 1.
A valve recess 106 is disposed near the periphery of the piston head top surface 104 at the center of the valve head 04, and the cavity 107 and the valve recess 106 are communicated with each other. It is being introduced to.

【０００３】この種の燃焼室では、吸気工程でスワール
ポート１０３からシリンダ内に導入された吸気により、
シリンダ内にシリンダ中心軸線１０９を旋回中心とする
スワール流１２３が形成され、圧縮工程の終期には、ピ
ストンヘッド頂面１０４がシリンダヘッドに接近するた
め、スワール流１２３がバルブリセス内周面１１２の案
内でキャビティ１０７内に速やかに導入され、キャビテ
ィ１０７内にキャビティ中心軸線１２２を旋回中心とす
る旋回流１２４が形成されるうえ、スキッシュ面１０５
によってキャビティ１０７内にスキッシュ流１２５が形
成され、この旋回流１２４とスキッシュ流１２５によっ
てキャビティ１０７内で空気と燃料１０８とが混合され
る。In this type of combustion chamber, the intake air introduced into the cylinder from the swirl port 103 in the intake process causes
A swirl flow 123 is formed in the cylinder around the center axis 109 of the cylinder, and at the end of the compression process, the top surface 104 of the piston head approaches the cylinder head, so that the swirl flow 123 guides the inner peripheral surface 112 of the valve recess. In this way, a swirling flow 124 is formed in the cavity 107 around the center axis 122 of the cavity, and the squish surface 105 is formed.
Thus, a squish flow 125 is formed in the cavity 107, and the swirl flow 124 and the squish flow 125 mix the air and the fuel 108 in the cavity 107.

【０００４】この従来技術では、キャビティ１０７の内
底面が平坦になっているため、キャビティ１０７の中心
部に旋回流１２４が作用しない空気の停滞部分が残る。In this prior art, since the inner bottom surface of the cavity 107 is flat, a stagnant portion of the air where the swirling flow 124 does not act remains at the center of the cavity 107.

【０００５】[0005]

【発明が解決しようとする課題】上記従来技術では、キ
ャビティ１０７の中心部に旋回流１２４が作用しない空
気の停滞部分が残るため、キャビティ１０７内での空気
と燃料１０８との混合が不十分となり、燃焼効率が低
い。In the above prior art, since a stagnant portion of air in which the swirling flow 124 does not act remains in the center of the cavity 107, mixing of the air and fuel 108 in the cavity 107 becomes insufficient. , Low combustion efficiency.

【０００６】本発明の課題は、燃焼効率を高めることが
できる、ディーゼルエンジンの直接噴射式燃焼室を提供
することにある。[0006] It is an object of the present invention to provide a direct injection combustion chamber for a diesel engine capable of improving the combustion efficiency.

【０００７】[0007]

【課題を解決するための手段】（第１発明と第２発明) 第１発明は、図１（Ａ）または図３に示すように、シリ
ンダヘッド１に燃料噴射ノズル２とスワールポート３と
を設け、ピストンヘッド頂面４に、スキッシュ面５を残
してバルブリセス６と燃焼用のキャビティ７とを凹設
し、キャビティ７内に燃料噴射ノズル２から燃料８を噴
射するようにし、キャビティ７をピストンヘッド頂面４
の中央部に、バルブリセス６をピストンヘッド頂面４の
周縁寄りにそれぞれ配置するとともに、キャビティ７と
バルブリセス６とを相互に連通させて、スワール流２３
がバルブリセス内周面１２の案内でキャビティ７に導入
されるようにした、ディーゼルエンジンの直接噴射式燃
焼室において、次のようにしたことを特徴とする。(First Invention and Second Invention ) According to a first invention, as shown in FIG. 1A or FIG. 3, a fuel injection nozzle 2 and a swirl port 3 are provided in a cylinder head 1. A valve recess 6 and a cavity 7 for combustion are recessed in the piston head top surface 4 while leaving a squish surface 5 so that fuel 8 is injected from the fuel injection nozzle 2 into the cavity 7. Head top surface 4
The valve recess 6 is arranged near the periphery of the piston head top surface 4 at the center of the swirl flow 23, and the cavity 7 and the valve recess 6 communicate with each other.
Is introduced into the cavity 7 through the guide of the inner peripheral surface 12 of the valve recess in a direct injection combustion chamber of a diesel engine, as described below.

【０００８】すなわち、キャビティ７の内底中央部から
シリンダヘッド１に向けて***部１０を形成し、 バルブ
リセス６を一個のみ設け、シリンダ中心軸線９と平行な
向きに見て、シリンダ中心軸線９からバルブリセス６の
リセス中心軸線１４に向けて伸びるリセス中心向き放射
仮想線１５と、シリンダ中心軸線９からリセス中心向き
放射仮想線１５と反対側に伸びる基準放射仮想線１６
と、基準放射仮想線１６からスワール流旋回方向に進角
させた下限放射仮想線１７と、この下限放射仮想線１７
よりも更にスワール流旋回方向に進角させた上限放射仮
想線１８とを想定し、 基準放射仮想線１６からの下限放
射仮想線１７の進角度１９を３０゜とし、基準放射仮想
線１６からの上限放射仮想線１８の進角度２０を１５０
゜とし、下限放射仮想線１７と上限放射仮想線１８との
間に挟まれた中心角１２０゜の扇形領域２１内に、シリ
ンダ中心軸線９から偏心させたキャビティ中心軸線２２
を配置した、ことを特徴とする。 また、第２発明は、第
１発明において、 基準放射仮想線１６からの下限放射仮
想線１７の進角度１９を３０゜とし、基準放射仮想線１
６からの上限放射仮想線１８の進角度２０を１５０゜と
し、下限放射仮想線１７と上限放射仮想線１８との間に
挟まれた中心角１２０゜の扇形領域２１内に、シリンダ
中心軸線９から偏心させたキャビティ中心軸線２２を配
置した、ことに代えて、 基準放射仮想線１６からの下限
放射仮想線１７の進角度１９を４５゜とし、基準放射仮
想線１６からの上限放射仮想線１８の進角度２０を１３
５゜とし、下限 放射仮想線１７と上限放射仮想線１８と
の間に挟まれた中心角９０゜の扇形領域２１内に、シリ
ンダ中心軸線９から偏心させたキャビティ中心軸線２２
を配置した、ことを特徴とする。 Namely, the ridge 10 is formed toward the inner bottom center portion of the cavity 7 in the cylinder head 1, the valve
Only one recess 6 is provided and is parallel to the cylinder center axis 9.
Viewed from the direction, the cylinder recess
Radiation toward recess center extending toward recess center axis 14
From the imaginary line 15 and the cylinder center axis 9 to the recess center
Reference radiation virtual line 16 extending to the opposite side of radiation virtual line 15
From the reference radiation virtual line 16 in the swirl swirling direction
The lower limit radiation virtual line 17 and the lower limit radiation virtual line 17
Upper limit radiation temporally advanced in swirl direction
Assuming the imaginary line 18, the lower limit emission from the reference emission virtual line 16 is performed.
The advance angle 19 of the virtual imaginary line 17 is set to 30 °, and the reference radiation virtual
The advance angle 20 of the upper limit imaginary line 18 from the line 16 is set to 150
の, the lower limit virtual emission line 17 and the upper limit virtual emission line 18
In the fan-shaped area 21 with a central angle of 120 ° sandwiched between
Cavity center axis 22 eccentric from cylinder center axis 9
Are arranged. In addition, the second invention provides a
In one invention, the lower limit radiation temporary from the reference radiation virtual line 16
The advance angle 19 of the imaginary line 17 is 30 °, and the reference radiation virtual line 1
The advance angle 20 of the upper limit imaginary line 18 from 6 is set to 150 °.
And between the lower virtual imaginary line 17 and the upper virtual imaginary line 18
In the fan-shaped area 21 having a central angle of 120 ° sandwiched between the cylinders,
A cavity center axis 22 eccentric from the center axis 9 is arranged.
Instead of the lower limit from the reference radiation virtual line 16
The advance angle 19 of the radiation virtual line 17 is set to 45 °, and the reference radiation temporary
The advance angle 20 of the upper limit radiation virtual line 18 from the imaginary line 16 is set to 13
5 °, and the lower limit radiation virtual line 17 and the upper limit radiation virtual line 18
In the fan-shaped region 21 with a central angle of 90 ° sandwiched between
Cavity center axis 22 eccentric from cylinder center axis 9
Are arranged.

【０００９】（第３発明） 第３発明は、第１発明または第２発明において、図３に
示すように、キャビティ内周面１１とバルブリセス内周
面１２とを、これらの接線方向に向けたスワール流案内
面１３で接続したことを特徴とする。( Third Invention) According to a third invention, in the first invention or the second invention , as shown in FIG. 3, the inner peripheral surface 11 of the cavity and the inner peripheral surface 12 of the valve recess are directed in a tangential direction thereof. It is characterized in that it is connected by a swirl flow guide surface 13.

【００１２】[0012]

【作用】（第１発明） この種の燃焼室では、図１（Ａ）または図３に示すよう
に、吸気工程でスワールポート３からシリンダ内に導入
された吸気により、シリンダ内にシリンダ中心軸線９を
旋回中心とするスワール流２３が形成され、圧縮工程の
終期には、ピストンヘッド頂面４がシリンダヘッド１に
接近するため、スワール流２３がバルブリセス内周面１
２の案内でキャビティ７内に速やかに導入され、キャビ
ティ７内にキャビティ中心軸線２２を旋回中心とする旋
回流２４が形成されるうえ、スキッシュ面５によってキ
ャビティ７内にスキッシュ流２５が形成され、この旋回
流２４とスキッシュ流２５によってキャビティ７内で空
気と燃料８とが混合される。(First Invention) In this type of combustion chamber, as shown in FIG. 1 (A) or FIG. 3, the intake air introduced into the cylinder from the swirl port 3 in the intake process causes the cylinder center axis to move into the cylinder. A swirl flow 23 is formed around the swirl center 9, and at the end of the compression process, the piston head top surface 4 approaches the cylinder head 1.
2, the squish flow 5 is quickly introduced into the cavity 7, the swirl flow 24 having the cavity center axis 22 as the center of rotation is formed in the cavity 7, and the squish surface 5 forms the squish flow 25 in the cavity 7. The air and the fuel 8 are mixed in the cavity 7 by the swirling flow 24 and the squish flow 25.

【００１３】そして、この第１発明では、キャビティ７
の内底中央部からシリンダヘッドに向けて***１０を形
成してあるため、キャビティ７の中心部に旋回流２４が
作用しない空気の停滞部分が無くなる。また、第１発明
では、次のように作用する。 すなわち、図１（Ａ）また
は図３に示すように、バルブリセス６からスワール流旋
回方向に沿って基準放射仮想線１６に至る前半部２６
と、基準放射仮想線１６からスワール流旋回方向に沿っ
てバルブリセス６に至る後半部２７とに、スキッシュ面
５を区分した場合、シリンダ中心軸線９からのキャビテ
ィ中心軸線２２ の偏心距離が一定ならば、基準放射仮想
線１６からスワール流下流側に９０゜進角させた直角放
射仮想線２８上にキャビティ中心軸線２２が位置する
時、前半部２６の面積が最大になり、かつ、後半部２７
の面積が最小になる。 このため、この直角放射仮想線２
８からスワール流２３の上流側と下流側とにそれぞれ均
等に広がる中心角１２０゜の扇形領域２１内に、キャビ
ティ中心軸線２２を配置すると、前半部２６の面積が十
分に大きく、後半部２７の面積が十分に小さくなり、前
半部２６で形成されるスキッシュ流２５が高速化される
分だけ、後半部２７で形成されるスキッシュ流２５が低
速化される。このため、バルブリセス６からキャビティ
７に導入された直後の旋回力の高い旋回流２４と高速の
スキッシュ流２５とがバランスよく複合化されるととも
に、キャビティ７内を半周程度旋回して旋回力がやや低
下した旋回流２４と低速のスキッシュ流２５とがバラン
スよく複合化され、スキッシュ流２５による旋回流２４
の乱れが起こりにくく、その旋回力の低下が抑制され
る。 In the first invention, the cavity 7
Since the bulge 10 is formed from the center of the inner bottom toward the cylinder head, there is no stagnant portion of the air where the swirling flow 24 does not act at the center of the cavity 7. Also, the first invention
Then, it works as follows. That is, FIG.
Is swirled from the valve recess 6 as shown in FIG.
First half 26 leading to reference radiation virtual line 16 along the turning direction
Along the swirl swirl direction from the reference radiation virtual line 16
Squish surface in the second half 27 leading to valve recess 6
5 is divided from the cylinder center axis 9
If the eccentric distance of the center axis 22 is constant, the reference radiation virtual
A 90 ° angle advance from line 16 downstream of the swirl flow
The cavity center axis 22 is located on the imaginary line 28
At the time, the area of the first half 26 is maximized, and the second half 27
Area is minimized. Therefore, this perpendicular radiation virtual line 2
8 to the upstream and downstream sides of the swirl flow 23, respectively.
In the fan-shaped area 21 with a central angle of 120 °
When the tee center axis 22 is arranged, the area of the first half 26 is sufficient.
Large enough, the area of the rear half 27 becomes sufficiently small,
The speed of the squish flow 25 formed by the half 26 is increased.
The squish flow 25 formed in the second half 27 is low
Be speeded up. Therefore, the cavity from the valve recess 6
7 and the high-speed swirling flow 24
With the squish flow 25 being compounded in a well-balanced manner
In addition, the turning force is slightly low by turning around half a circle in the cavity 7.
The swirling flow 24 and the low-speed squish flow 25 are balanced
Swirling flow 24 by squish flow 25
Turbulence does not easily occur, and the reduction of the turning force is suppressed.
You.

【００１４】（第３発明） 第３発明では、第１発明の作用に加え、次のように作用
する。すなわち、図３に示すように、バルブリセス６に
導入されたスワール流２３が、スワール流案内面１３に
沿ってキャビティ７内に速やかに案内され、キャビティ
７内の旋回流２４の流速が高まる。( Third invention) In the third invention, in addition to the operation of the first invention, the following operation is performed. That is, as shown in FIG. 3, the swirl flow 23 introduced into the valve recess 6 is quickly guided into the cavity 7 along the swirl flow guide surface 13, and the flow velocity of the swirl flow 24 in the cavity 7 increases.

【００１７】[0017]

【発明の効果】（第１発明または第２発明） 第１発明または第２発明では、キャビティ７内に旋回流
２４が作用しない空気の停滞部分が無くなるため、キャ
ビティ７内での空気と燃料８との混合が促進され、燃焼
効率が高まる。また、スキッシュ流２５による旋回流２
４の乱れが起こりにくく、その旋回力の低下が抑制され
るため、キャビティ７内での空気と燃料８の混合が一層
促進され、燃焼効率が一層高まる。 According to the first and second aspects of the present invention , since there is no stagnant portion of the air in which the swirling flow 24 does not act in the cavity 7, the air and the fuel 8 in the cavity 7 are eliminated. Is promoted, and the combustion efficiency is increased. In addition, swirl flow 2 by squish flow 25
4 is less likely to be disturbed, and a decrease in the turning force is suppressed.
Therefore, the mixing of the air and the fuel 8 in the cavity 7 is further improved.
Promoted and the combustion efficiency is further increased.

【００１８】（第３発明） 第３発明では、第１発明または第２発明の効果に加え、
次の効果を奏する。すなわち、キャビティ７内の旋回流
２４の流速が高まるため、キャビティ７内での空気と燃
料８の混合が一層促進され、燃焼効率が一層高まる。( Third invention) In the third invention, in addition to the effects of the first invention or the second invention ,
The following effects are obtained. That is, since the flow velocity of the swirling flow 24 in the cavity 7 increases, the mixing of the air and the fuel 8 in the cavity 7 is further promoted, and the combustion efficiency further increases.

【００２０】[0020]

【発明の実施の形態】本発明の実施の形態を図面に基づ
いて説明する。図１及び図２に示す第１実施形態では、
単気筒の横形ディーゼルエンジンを用いている。このエ
ンジンの構成は次の通りである。すなわち、図２（Ａ）
に示すように、シリンダブロック２９内にシリンダ３０
を水平な向きに設け、シリンダブロック２９の一端側に
シリンダヘッド１を組み付けてある。シリンダ３０には
ピストンヘッド３２を内嵌してある。そして、シリンダ
ブロック２９とシリンダヘッド１とにわたってプッシュ
ロッド挿通孔３４をあけ、ここにプッシュロッド３５を
挿通してある。シリンダヘッド１には、吸気用のスワー
ルポート３と排気ポート３１と、ノズル差し込み孔３３
とを設け、ノズル差し込み孔３３に燃料噴射ノズル２を
差し込んで固定してある。Embodiments of the present invention will be described with reference to the drawings. In the first embodiment shown in FIGS. 1 and 2,
A single cylinder horizontal diesel engine is used. The structure of this engine is as follows. That is, FIG.
As shown in FIG.
Are provided in a horizontal direction, and the cylinder head 1 is attached to one end of the cylinder block 29. A piston head 32 is fitted in the cylinder 30. A push rod insertion hole 34 is formed between the cylinder block 29 and the cylinder head 1, and a push rod 35 is inserted through the hole 34. The cylinder head 1 has a swirl port 3 for intake, an exhaust port 31, and a nozzle insertion hole 33.
The fuel injection nozzle 2 is inserted into the nozzle insertion hole 33 and fixed.

【００２１】そして、図１に示すように、ピストンヘッ
ド頂面４に、スキッシュ面５を残してバルブリセス６と
燃焼用のキャビティ７とを凹設し、キャビティ７内に燃
料噴射ノズル２から燃料８を噴射するようにし、キャビ
ティ７をピストンヘッド頂面４の中央部に、バルブリセ
ス６をピストンヘッド頂面４の周縁寄りにそれぞれ配置
するとともに、キャビティ７とバルブリセス６とを相互
に連通させて、スワール流２３がバルブリセス内周面１
２の案内でキャビティ７に導入されるようにしてある。As shown in FIG. 1, a valve recess 6 and a combustion cavity 7 are recessed in the piston head top surface 4 while leaving a squish surface 5. The cavity 7 is arranged at the center of the piston head top surface 4, the valve recess 6 is arranged near the periphery of the piston head top surface 4, respectively, and the cavity 7 and the valve recess 6 are communicated with each other to form a swirl. Flow 23 is inner peripheral surface 1 of valve recess
2 to be introduced into the cavity 7.

【００２２】この種の燃焼室では、吸気工程でスワール
ポート３からシリンダ内に導入された吸気により、シリ
ンダ内にシリンダ中心軸線９を旋回中心とするスワール
流２３が形成され、圧縮工程の終期には、ピストンヘッ
ド頂面４がシリンダヘッド１に接近するため、スワール
流２３がバルブリセス内周面１２の案内でキャビティ７
内に速やかに導入され、キャビティ７内にキャビティ中
心軸線２２を旋回中心とする旋回流２４が形成されるう
え、スキッシュ面５によってキャビティ７内にスキッシ
ュ流２５が形成され、この旋回流２４とスキッシュ流２
５によってキャビティ７内で空気と燃料８とが混合され
る。In this type of combustion chamber, a swirl flow 23 centering on the cylinder center axis 9 is formed in the cylinder by the intake air introduced into the cylinder from the swirl port 3 in the intake process, and at the end of the compression process. Since the top surface 4 of the piston head approaches the cylinder head 1, the swirl flow 23 is guided by the inner peripheral surface 12 of the valve recess to form the cavity 7.
The squish surface 5 forms a squish flow 25 in the cavity 7, and the squish surface 5 forms a squish flow 25 in the cavity 7. Stream 2
5 mixes air and fuel 8 in the cavity 7.

【００２３】この実施形態では、燃焼効率を高めるた
め、キャビティ７の内底中央部からシリンダヘッド１に
向けて***部１０を形成してあるため、キャビティ７の
中心部に旋回流２４が作用しない空気の停滞部分が無く
なり、キャビティ７内での空気と燃料との混合が促進さ
れ、燃焼効率が高まる。In this embodiment, the raised portion 10 is formed from the center of the inner bottom of the cavity 7 toward the cylinder head 1 in order to increase the combustion efficiency. Therefore, the swirling flow 24 does not act on the center of the cavity 7. The stagnant portion of the air is eliminated, the mixing of the air and the fuel in the cavity 7 is promoted, and the combustion efficiency is increased.

【００２４】バルブリセス６は円形にしてある。このバ
ルブリセス６は、吸気バルブ用のバルブリセスで、排気
バルブ用のバルブリセスは設けていない。燃料噴射ノズ
ル２から噴射される燃料８は、キャビティ中心軸線２２
付近からキャビティ内周面１１に向けてある。キャビテ
ィ７はシリンダ中心軸線９と平行なキャビティ中心軸線
２２を有し、キャビティ内周面１１はキャビティ７の内
底面に近づくにつれて次第に径を広げる円錐台面として
ある。また、***部１０の周面は、シリンダヘッド１に
近づくにつれて次第に径を広げる円錐面としてある。図
１（Ｄ）に示すように、シリンダ中心軸線９と直交する
仮想断面上で、キャビティ内周面１１と***部１０の周
面とは、キャビティ中心軸線２２を中心とする同心円に
なるため、キャビティ７内で旋回流２４が抵抗少なく旋
回する。The valve recess 6 is circular. The valve recess 6 is a valve recess for an intake valve, and has no valve recess for an exhaust valve. The fuel 8 injected from the fuel injection nozzle 2 is supplied to the cavity center axis 22.
It is directed from the vicinity to the inner circumferential surface 11 of the cavity. The cavity 7 has a cavity center axis 22 parallel to the cylinder center axis 9, and the cavity inner peripheral surface 11 is a truncated conical surface whose diameter gradually increases as approaching the inner bottom surface of the cavity 7. The peripheral surface of the raised portion 10 is a conical surface whose diameter gradually increases as approaching the cylinder head 1. As shown in FIG. 1D, on a virtual cross section orthogonal to the cylinder center axis 9, the inner circumferential surface 11 of the cavity and the circumferential surface of the raised portion 10 are concentric circles centered on the center axis 22 of the cavity. The swirling flow 24 swirls in the cavity 7 with low resistance.

【００２５】この第１実施形態では、図１（Ａ）に示す
ように、バルブリセス６を一個のみ設け、シリンダ中心
軸線９と平行な向きに見て、シリンダ中心軸線９からバ
ルブリセス６のリセス中心軸線１４に向けて伸びるリセ
ス中心向き放射仮想線１５と、シリンダ中心軸線９から
リセス中心向き放射仮想線１５と反対側に伸びる基準放
射仮想線１６と、基準放射仮想線１６からスワール流旋
回方向に進角させた下限放射仮想線１７と、この下限放
射仮想線１７よりも更にスワール流旋回方向に進角させ
た上限放射仮想線１８とを想定した。In the first embodiment, as shown in FIG. 1A, only one valve recess 6 is provided, and when viewed in a direction parallel to the cylinder center axis 9, the recess center axis of the valve recess 6 extends from the cylinder center axis 9. 14, a virtual imaginary line 15 extending toward the center of the recess extending toward the recess 14, a virtual imaginary line 16 extending from the cylinder center axis 9 to the opposite side to the virtual imaginary line 15 toward the center of the recess, and a swirl flow turning direction from the standard virtual imaginary line 16. An assumed lower-limit emission virtual line 17 and an upper-limit emission virtual line 18 advanced further in the swirl flow turning direction than the lower limit emission virtual line 17 are assumed.

【００２６】そして、基準放射仮想線１６からの下限放
射仮想線１７の進角度１９を３０゜とし、基準放射仮想
線１６からの上限放射仮想線１８の進角度２０を１５０
゜とし、下限放射仮想線１７と上限放射仮想線１８との
間に挟まれた中心角１２０゜の扇形領域２１内に、シリ
ンダ中心軸線９から偏心させたキャビティ中心軸線２２
を配置した。The advance angle 19 of the lower limit virtual emission line 17 from the reference emission virtual line 16 is 30 °, and the advance angle 20 of the upper limit emission virtual line 18 from the reference emission virtual line 16 is 150 °.
And a cavity center axis 22 eccentric from the cylinder center axis 9 in a sector area 21 having a center angle 120 ° sandwiched between the lower limit radiation virtual line 17 and the upper limit radiation virtual line 18.
Was placed.

【００２７】このような構成によれば、バルブリセス６
からスワール流旋回方向に沿って基準放射仮想線１６に
至る前半部２６と、基準放射仮想線１６からスワール流
旋回方向に沿ってバルブリセス６に至る後半部２７と
に、スキッシュ面５を区分した場合、シリンダ中心軸線
９からのキャビティ中心軸線２２の偏心距離が一定なら
ば、基準放射仮想線１６からスワール流下流側に９０゜
進角させた直角放射仮想線２８上にキャビティ中心軸線
２２が位置する時、前半部２６の面積が最大になり、か
つ、後半部２７の面積が最小になる。According to such a configuration, the valve recess 6
When the squish surface 5 is divided into a first half 26 from the imaginary line to the reference radiation virtual line 16 along the swirl flow turning direction, and a second half 27 from the reference radiation virtual line 16 to the valve recess 6 along the swirl flow turning direction. If the eccentric distance of the cavity center axis 22 from the cylinder center axis 9 is constant, the cavity center axis 22 is located on a right-angle virtual imaginary line 28 which is advanced from the reference virtual imaginary line 16 by 90 ° downstream of the swirl flow. At this time, the area of the front half 26 is maximized, and the area of the rear half 27 is minimized.

【００２８】このため、この直角放射仮想線２８からス
ワール流２３の上流側と下流側とにそれぞれ均等に広が
る中心角１２０゜の扇形領域２１内に、キャビティ中心
軸線２２を配置すると、前半部２６の面積が十分に大き
く、後半部２７の面積が十分に小さくなり、前半部２６
で形成されるスキッシュ流２５が高速化される分だけ、
後半部２７で形成されるスキッシュ流２５が低速化され
る。このため、バルブリセス６からキャビティ７に導入
された直後の旋回力の高い旋回流２４と高速のスキッシ
ュ流２５とがバランスよく複合化されるとともに、キャ
ビティ７内を半周程度旋回して旋回力がやや低下した旋
回流２４と低速のスキッシュ流２５とがバランスよく複
合化され、スキッシュ流２５による旋回流２４の乱れが
起こりにくく、その旋回力の低下が抑制される。このた
め、キャビティ７内での空気と燃料８の混合が一層促進
され、燃焼効率が一層高まる。For this reason, when the cavity center axis 22 is disposed in the sectoral area 21 having a central angle of 120 ° that spreads equally from the right-angled imaginary line 28 to the upstream side and the downstream side of the swirl flow 23, the front half 26 Is sufficiently large, the area of the rear half 27 is sufficiently small, and the area of the front half 26 is small.
As much as the speed of the squish flow 25 formed by
The speed of the squish flow 25 formed in the rear half 27 is reduced. Therefore, the swirling flow 24 having a high swirling force and the high-speed squish flow 25 immediately after being introduced from the valve recess 6 into the cavity 7 are combined in a well-balanced manner. The reduced swirl flow 24 and the low-speed squish flow 25 are combined in a well-balanced manner, and the squish flow 25 is less likely to disturb the swirl flow 24, thereby suppressing a decrease in the swirling force. Therefore, the mixing of the air and the fuel 8 in the cavity 7 is further promoted, and the combustion efficiency is further increased.

【００２９】より望ましくは、基準放射仮想線１６から
の下限放射仮想線１７の進角度１９を４５゜とし、基準
放射仮想線１６からの上限放射仮想線１８の進角度２０
を１３５゜とし、下限放射仮想線１７と上限放射仮想線
１８との間に挟まれた中心角９０゜の扇形領域２１内に
シリンダ中心軸線９から偏心させたキャビティ中心軸線
２２を配置する。More preferably, the advancing angle 19 of the lower limit virtual emission line 17 from the reference emission virtual line 16 is 45 °, and the advancing angle 20 of the upper limit emission virtual line 18 from the reference emission virtual line 16 is
Is set to 135 °, and the cavity center axis 22 eccentric from the cylinder center axis 9 is arranged in a sector area 21 having a center angle of 90 ° sandwiched between the lower limit radiation virtual line 17 and the upper limit radiation virtual line 18.

【００３０】図３に示す第２実施形態では、図１及び図
２に示す第１実施形態において、キャビティ内周面１１
とバルブリセス内周面１２とを、これらの接線方向に向
けたスワール流案内面１３で接続してある。他の構成は
第１実施形態と同一にしており、図３中、第１実施形態
と同一の要素には同一の符号を付しておく。このような
構成によれば、バルブリセス６に導入されたスワール流
２３が、スワール流案内面１３に沿ってキャビティ７内
に速やかに案内され、キャビティ７内の旋回流２４の流
速が高まる。このため、キャビティ７内での空気と燃料
８の混合が一層促進され、燃焼効率が一層高まる。In the second embodiment shown in FIG. 3, in the first embodiment shown in FIGS.
And the inner peripheral surface 12 of the valve recess are connected by a swirl flow guiding surface 13 directed in the tangential direction. The other configuration is the same as that of the first embodiment. In FIG. 3, the same elements as those of the first embodiment are denoted by the same reference numerals. According to such a configuration, the swirl flow 23 introduced into the valve recess 6 is quickly guided into the cavity 7 along the swirl flow guide surface 13, and the flow velocity of the swirl flow 24 in the cavity 7 increases. Therefore, the mixing of the air and the fuel 8 in the cavity 7 is further promoted, and the combustion efficiency is further increased.

【図面の簡単な説明】[Brief description of the drawings]

【図１】第１実施形態の燃焼室を説明する図で、図１
（Ａ）はピストンヘッド頂面の正面図、図１（Ｂ）は図
１（Ａ）のＢ−Ｂ線断面図、図１（Ｃ）は図１（Ａ）の
Ｃ−Ｃ線断面図、図１（Ｄ）は図１（Ｂ）のＤ−Ｄ線断
面図である。FIG. 1 is a diagram illustrating a combustion chamber according to a first embodiment;
(A) is a front view of the top surface of the piston head, FIG. 1 (B) is a sectional view taken along line BB of FIG. 1 (A), FIG. 1 (C) is a sectional view taken along line CC of FIG. 1 (A), FIG. 1D is a sectional view taken along line DD of FIG. 1B.

【図２】第１実施形態の燃焼室を備えたエンジンの要部
説明図で、図２（Ａ）は縦断側面図、図２（Ｂ）は図２
（Ａ）のＢ−Ｂ線断面図である。FIG. 2 is an explanatory view of a main part of an engine including a combustion chamber according to the first embodiment, wherein FIG. 2 (A) is a longitudinal side view, and FIG.
It is a BB sectional view taken on the line of (A).

【図３】第２実施形態の燃焼室に用いるピストンヘッド
頂面の正面図である。FIG. 3 is a front view of a top surface of a piston head used in a combustion chamber according to a second embodiment.

【図４】従来技術の燃焼室を説明する図で、図４（Ａ）
はピストンヘッド頂面の正面図、図４（Ｂ）は図４
（Ａ）のＢ−Ｂ線断面図である。FIG. 4 is a view for explaining a conventional combustion chamber, and FIG.
4B is a front view of the top surface of the piston head, and FIG.
It is a BB sectional view taken on the line of (A).

【符号の説明】[Explanation of symbols]

１…シリンダヘッド、２…燃料噴射ノズル、３…スワー
ルポート、４…ピストンヘッド頂面、５…スキッシュ
面、６…バルブリセス、７…キャビティ、８…燃料、９
…シリンダ中心軸線、１０…***部、１１…キャビティ
内周面、１２…バルブリセス内周面、１３…スワール流
案内面、１４…リセス中心軸線、１５…リセス中心向き
放射仮想線、１６…基準放射仮想線、１７…下限放射仮
想線、１８…上限放射仮想線、１９・２０…進角度、２
１…扇形領域、２２…キャビティ中心軸線、２３…スワ
ール流。DESCRIPTION OF SYMBOLS 1 ... Cylinder head, 2 ... Fuel injection nozzle, 3 ... Swirl port, 4 ... Piston head top surface, 5 ... Squish surface, 6 ... Valve recess, 7 ... Cavity, 8 ... Fuel, 9
... Cylinder central axis, 10 ... Protrusion, 11 ... Cavity inner peripheral surface, 12 ... Valve recess inner peripheral surface, 13 ... Swirl flow guide surface, 14 ... Recess central axis, 15 ... Recess central emission line, 16 ... Reference radiation Virtual line, 17: Lower limit virtual line, 18: Upper limit virtual line, 19/20: Advance angle, 2
1 ... sector region, 22 ... cavity center axis line, 23 ... swirl flow.

フロントページの続き (51)Int.Cl.7 識別記号 ＦＩ Ｆ０２Ｆ 3/28 Ｆ０２Ｆ 3/28 Ｂ (56)参考文献 特開 昭58−35223（ＪＰ，Ａ) 特開 昭56−38517（ＪＰ，Ａ) 特開 昭60−224920（ＪＰ，Ａ) 実開 昭57−25117（ＪＰ，Ｕ) 実開 昭58−72424（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F02B 23/06 F02F 3/26 F02F 3/28 Continuation of the front page (51) Int.Cl. 7 Identification symbol FI F02F 3/28 F02F 3/28 B (56) References JP-A-58-35223 (JP, A) JP-A-56-38517 (JP, A JP-A-60-224920 (JP, A) JP-A-57-25117 (JP, U) JP-A-58-72424 (JP, U) (58) Fields investigated (Int. Cl. 7 , DB name) F02B 23/06 F02F 3/26 F02F 3/28

Claims (3)

(57)【特許請求の範囲】(57) [Claims] 【請求項１】 シリンダヘッド(１)に燃料噴射ノズル
(２)とスワールポート(３)とを設け、ピストンヘッド頂
面(４)に、スキッシュ面(５)を残してバルブリセス(６)
と燃焼用のキャビティ(７)とを凹設し、キャビティ(７)
内に燃料噴射ノズル(２)から燃料(８)を噴射するように
し、キャビティ(７)をピストンヘッド頂面(４)の中央部
に、バルブリセス(６)をピストンヘッド頂面(４)の周縁
寄りにそれぞれ配置するとともに、キャビティ(７)とバ
ルブリセス(６)とを相互に連通させて、スワール流(２
３)がバルブリセス内周面(１２)の案内でキャビティ
(７)に導入されるようにした、ディーゼルエンジンの直
接噴射式燃焼室において、 キャビティ(７)の内底中央部からシリンダヘッド(１)に
向けて***部(１０)を形成し、 バルブリセス(６)を一個のみ設け、シリンダ中心軸線
(９)と平行な向きに見て、シリンダ中心軸線(９)からバ
ルブリセス(６)のリセス中心軸線(１４)に向けて伸びる
リセス中心向き放射仮想線(１５)と、シリンダ中心軸線
(９)からリセス中心向き放射仮想線(１５)と反対側に伸
びる基準放射仮想線(１６)と、基準放射仮想線(１６)か
らスワール流旋回方向に進角させた下限放射仮想線(１
７)と、この下限放射仮想線(１７)よりも更にスワール
流旋回方向に進角させた上限放射仮想線(１８)とを想定
し、 基準放射仮想線(１６)からの下限放射仮想線(１７)の進
角度(１９)を３０゜とし、基準放射仮想線(１６)からの
上限放射仮想線(１８)の進角度(２０)を１５０゜とし、
下限放射仮想線(１７)と上限放射仮想線(１８)との間に
挟まれた中心角１２０゜の扇形領域(２１)内に、シリン
ダ中心軸線９から偏心させたキャビティ中心軸線(２２)
を配置した、 ことを特徴とするディーゼルエンジンの直
接噴射式燃焼室。A fuel injection nozzle is provided on a cylinder head (1).
(2) and a swirl port (3) are provided, and a valve recess (6) is left on the piston head top surface (4) while leaving a squish surface (5).
And a cavity (7) for combustion, and a cavity (7)
The fuel (8) is injected from the fuel injection nozzle (2), the cavity (7) is in the center of the piston head top surface (4), and the valve recess (6) is the periphery of the piston head top surface (4). And the cavity (7) and the valve recess (6) communicate with each other to form a swirl flow (2).
3) The cavity is guided by the inner peripheral surface (12) of the valve recess.
In a direct injection combustion chamber of a diesel engine, which is introduced into (7), a raised portion (10) is formed from the center of the inner bottom of the cavity (7) toward the cylinder head (1), and the valve recess ( 6) Only one cylinder is provided
When viewed in a direction parallel to (9), the cylinder center axis (9)
Lubrices (6) extends towards the recess center axis (14)
Radiation imaginary line (15) directed to the center of the recess and the cylinder center axis
From (9), extend to the opposite side to the virtual imaginary line (15) toward the center of the recess.
The reference radiation virtual line (16) and the reference radiation virtual line (16)
Lower limit radiation imaginary line (1)
7) and swirl more than this lower limit radiation virtual line (17)
Assuming the upper limit radiation virtual line (18) advanced in the flow turning direction
Of the lower limit radiation virtual line (17) from the reference radiation virtual line (16).
The angle (19) is 30 °, and the angle from the reference radiation virtual line (16) is
The advance angle (20) of the upper limit radiation virtual line (18) is set to 150 °,
Between the lower radiation imaginary line (17) and the upper radiation imaginary line (18)
In the fan-shaped area (21) with a central angle of 120 °,
Cavity center axis (22) eccentric from damper center axis 9
It was placed, direct injection combustion chamber of a diesel engine, characterized in that. 【請求項２】 請求項１に記載したディーゼルエンジン
の直接噴射式燃焼室において、 基準放射仮想線(１６)からの下限放射仮想線(１７)の進
角度(１９)を３０゜と し、基準放射仮想線(１６)からの
上限放射仮想線(１８)の進角度(２０)を１５０゜とし、
下限放射仮想線(１７)と上限放射仮想線(１８)との間に
挟まれた中心角１２０゜の扇形領域(２１)内に、シリン
ダ中心軸線９から偏心させたキャビティ中心軸線(２２)
を配置した、ことに代えて、 基準放射仮想線(１６)からの下限放射仮想線(１７)の進
角度(１９)を４５゜とし、基準放射仮想線(１６)からの
上限放射仮想線(１８)の進角度(２０)を１３５゜とし、
下限放射仮想線(１７)と上限放射仮想線(１８)との間に
挟まれた中心角９０゜の扇形領域(２１)内に、シリンダ
中心軸線９から偏心させたキャビティ中心軸線(２２)を
配置した、 ことを特徴とするディーゼルエンジンの直接
噴射式燃焼室。 2. The diesel engine according to claim 1.
In the direct injection combustion chamber, the lower limit radiation virtual line (17) from the reference radiation virtual line (16) advances.
The angle (19) is 30 °, and the angle from the reference radiation virtual line (16) is
The advance angle (20) of the upper limit radiation virtual line (18) is set to 150 °,
Between the lower radiation imaginary line (17) and the upper radiation imaginary line (18)
In the fan-shaped area (21) with a central angle of 120 °,
Cavity center axis (22) eccentric from damper center axis 9
Instead of the reference radiation imaginary line (16).
The angle (19) is 45 °, and the angle from the reference radiation virtual line (16) is
The advance angle (20) of the upper limit radiation virtual line (18) is set to 135 °,
Between the lower radiation imaginary line (17) and the upper radiation imaginary line (18)
In the sandwiched area (21) with a central angle of 90 °, the cylinder
The cavity center axis (22) decentered from the center axis 9
A direct injection combustion chamber for a diesel engine, which is arranged . 【請求項３】 請求項１または請求項２に記載したディ
ーゼルエンジンの直接噴射式燃焼室において、 キャビティ内周面(１１)とバルブリセス内周面(１２)と
を、これらの接線方向に向けたスワール流案内面(１３)
で接続した、ことを特徴とするディーゼルエンジンの直
接噴射式燃焼室。3. The direct injection combustion chamber of a diesel engine according to claim 1 , wherein the inner peripheral surface (11) of the cavity and the inner peripheral surface (12) of the valve recess are directed in a tangential direction thereof. Swirl flow guideway (13)
A direct-injection combustion chamber for a diesel engine, characterized by being connected by:
JP31993695A 1995-12-08 1995-12-08 Diesel engine direct injection combustion chamber Expired - Fee Related JP3357519B2 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP31993695A JP3357519B2 (en) 1995-12-08 1995-12-08 Diesel engine direct injection combustion chamber
CN96114585A CN1086443C (en) 1995-12-08 1996-11-22 Direct injection type combustion chamber of diesel engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP31993695A JP3357519B2 (en) 1995-12-08 1995-12-08 Diesel engine direct injection combustion chamber

Publications (2)

Publication Number Publication Date
JPH09158734A JPH09158734A (en) 1997-06-17
JP3357519B2 true JP3357519B2 (en) 2002-12-16

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ID=18115901

Family Applications (1)

Application Number Title Priority Date Filing Date
JP31993695A Expired - Fee Related JP3357519B2 (en) 1995-12-08 1995-12-08 Diesel engine direct injection combustion chamber

Country Status (2)

Country Link
JP (1) JP3357519B2 (en)
CN (1) CN1086443C (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007270749A (en) * 2006-03-31 2007-10-18 Toyota Motor Corp Internal combustion engine
CN101676538A (en) * 2008-09-18 2010-03-24 吕文杰 Engine with multiple-level gas displacement
US20150337756A1 (en) * 2013-01-07 2015-11-26 Toyota Jidosha Kabushiki Kaisha Internal combustion engine
JP6432788B2 (en) * 2015-07-29 2018-12-05 マツダ株式会社 Engine combustion chamber structure
CN112031920A (en) * 2020-09-11 2020-12-04 潍柴动力股份有限公司 Diesel engine combustion system and diesel engine

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN87210334U (en) * 1987-07-18 1988-07-20 大连工学院 Squeezing-and-flowing-nozzle type oil-film atomizing combustion chamber
CN2184785Y (en) * 1994-01-17 1994-12-07 云南内燃机厂 4100 energy saving type diesel engine

Also Published As

Publication number Publication date
CN1086443C (en) 2002-06-19
CN1152071A (en) 1997-06-18
JPH09158734A (en) 1997-06-17

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