JPS58166106A - Hydraulic cylinder device - Google Patents
Hydraulic cylinder deviceInfo
- Publication number
- JPS58166106A JPS58166106A JP4840682A JP4840682A JPS58166106A JP S58166106 A JPS58166106 A JP S58166106A JP 4840682 A JP4840682 A JP 4840682A JP 4840682 A JP4840682 A JP 4840682A JP S58166106 A JPS58166106 A JP S58166106A
- Authority
- JP
- Japan
- Prior art keywords
- piston
- cylinder
- pressure
- hydraulic
- low
- 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
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Actuator (AREA)
Abstract
Description
【発明の詳細な説明】
本発明は油圧シリンダに関し、例えばディーゼルエンジ
ンの燃料噴射装置に用いて有効である。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydraulic cylinder, and is effective for use in, for example, a fuel injection device for a diesel engine.
従来のこの種の油圧シリンダ1は第1図の如く構成され
ていたが、その油圧シリンダ1は低圧ピストン2がシリ
ンダヘッド4aに当接するまで移動する構成となってい
たため、エンジンが高速回転をし低圧ピストン2の動き
が早くなると、シリンダヘッド4aに衝突した際に低圧
ピストンがダンピングを生じるという問題があった。こ
のダンピングは高圧ピストン3を再び押すことになり噴
射を生じたり、低圧ピストン2の繰返しシリンダ4にあ
たる衝撃力によりシリンダヘッド4aを疲労破損させる
という欠点を有している。A conventional hydraulic cylinder 1 of this type was constructed as shown in Fig. 1, but the hydraulic cylinder 1 was constructed so that the low-pressure piston 2 moved until it came into contact with the cylinder head 4a, which caused the engine to rotate at high speed. When the low-pressure piston 2 moves quickly, there is a problem in that the low-pressure piston causes damping when it collides with the cylinder head 4a. This damping has the disadvantage that the high-pressure piston 3 is pushed again, resulting in injection, and that the repeated impact force of the low-pressure piston 2 on the cylinder 4 causes fatigue damage to the cylinder head 4a.
本考案は上記点に鑑みて案出されたもので、ピストン頭
部もしくはシリンダ端面に油圧孔の少なくとも一部を塞
ぐことの可能なパルプを設け、ピストンがシリンダ端面
に衝、突する以前に該パルプが油圧孔の少なくとも一部
を塞ぐことにより、シリンダとピストン間の圧力室の圧
力を上昇せしめ、ピストンに加わる力と、圧力室内の圧
力がバランスする位置にピストンを減速あるいは停止さ
せシリンダへの衝撃力を緩和し、ピストンのスムース(
2)
な運転を可能にすることを目的としている。The present invention has been devised in view of the above points, and includes a pulp that can block at least a portion of the hydraulic hole on the piston head or the cylinder end surface, so that the piston hits the cylinder end surface before it collides with the cylinder end surface. By blocking at least a portion of the hydraulic hole with the pulp, the pressure in the pressure chamber between the cylinder and the piston is increased, and the piston is decelerated or stopped at a position where the force applied to the piston and the pressure in the pressure chamber are balanced, and the pressure applied to the cylinder is increased. Reduces the impact force and makes the piston smoother (
2) The purpose is to enable safe driving.
以下本発明の一実施例を第2図により説明する。An embodiment of the present invention will be described below with reference to FIG.
油圧シリンダ装置lは、低圧ピストン2、高圧ピストン
3、シリンダ4より構成され、低圧ピストン2とシリン
ダ4の端面(シリンダヘッド4a)の間に低圧室5を形
成し、また高圧ピストンとシリンダ4の端面との間に高
圧室6が形成している。The hydraulic cylinder device 1 is composed of a low-pressure piston 2, a high-pressure piston 3, and a cylinder 4, and forms a low-pressure chamber 5 between the end face (cylinder head 4a) of the low-pressure piston 2 and the cylinder 4. A high pressure chamber 6 is formed between the end face and the end face.
低圧室5を形成するシリンダ4の端面には低圧油圧孔7
が穿設され、また高圧室6を形成するシリンダ4の端面
には高圧油圧孔8が設けである。そして、高圧油圧孔8
は途中で分岐しており、一方は、噴射ノズル9へ連通し
、他方はチェック弁10を介して燃料導入口11に連通
している。A low pressure hydraulic hole 7 is provided in the end face of the cylinder 4 that forms the low pressure chamber 5.
A high-pressure hydraulic hole 8 is provided in the end face of the cylinder 4 forming the high-pressure chamber 6. And high pressure hydraulic hole 8
is branched in the middle; one side communicates with the injection nozzle 9 and the other side communicates with the fuel inlet 11 via the check valve 10.
低圧ピストン2の頭部には低圧油圧孔7を塞ぐことの可
能なパルプ12が設けである。このパルプ12はスプリ
ング13により低圧ピストン2の頭部より突出する方向
に押圧されている。尤もパルプ12は低圧ピストン2よ
り抜けない様にストッパー14A、14Bにより係止さ
れており、従ってパルプ12の低圧ピストン2からの突
出スト(3)
ローフは決定されている。尚、ストッパー14Bはその
先端にねじが切ってあり、パルプ12に螺着固定される
。そして、パルプ12、スプリング13、及びストッパ
ー14A、14Bはホルダー15に組付けられた後、低
圧ピストン2に一体物として打込まれ固定されている。The head of the low-pressure piston 2 is provided with a pulp 12 that can close the low-pressure hydraulic hole 7. This pulp 12 is pressed by a spring 13 in the direction of protruding from the head of the low pressure piston 2. Of course, the pulp 12 is stopped by the stoppers 14A and 14B so that it does not come off the low pressure piston 2, and therefore, the stroke (3) loaf of the pulp 12 protruding from the low pressure piston 2 is determined. Note that the stopper 14B has a thread cut at its tip and is screwed and fixed to the pulp 12. After the pulp 12, spring 13, and stoppers 14A and 14B are assembled into the holder 15, they are driven into the low-pressure piston 2 as one piece and fixed therein.
ホルダー15には溝部16が設けてあり、スプリング室
17と低圧室5とはこの溝部16を介して導通している
。The holder 15 is provided with a groove 16, and the spring chamber 17 and the low pressure chamber 5 are electrically connected through the groove 16.
以上の如く構成した油圧シリンダーの作動を説明する。The operation of the hydraulic cylinder configured as above will be explained.
燃料噴射時期には、まず比較的低圧(例えば120〜1
70気圧)の燃料が低圧室5に低圧油圧孔7より圧送さ
れ、これによって低圧ピストン2が移動を開始する。低
圧ピストン2が高圧ピストン3を押し付ける結果、高圧
室6には高圧が生じ、この圧力が設定圧(例えば100
0気圧)以上になると噴射ノズル9から燃料が噴射され
る。At the time of fuel injection, first the pressure is relatively low (for example, 120 to 1
70 atmospheres) of fuel is fed under pressure to the low pressure chamber 5 from the low pressure hydraulic hole 7, and the low pressure piston 2 begins to move. As a result of the low-pressure piston 2 pressing against the high-pressure piston 3, high pressure is generated in the high-pressure chamber 6, and this pressure reaches the set pressure (for example, 100
When the pressure exceeds 0 atmospheric pressure), fuel is injected from the injection nozzle 9.
そして、燃料噴射が終了すれば低圧室5内の油圧を抜き
同時に高圧室6内へ燃料人口11からチλ
ニック弁を介して次回噴射する燃料が圧送される。When the fuel injection is completed, the oil pressure in the low pressure chamber 5 is removed, and at the same time, the fuel to be injected next time is pumped into the high pressure chamber 6 from the fuel supply 11 via the chinic valve.
(4)
従って高圧室6内へ導かれた燃料の圧力によって高圧ピ
ストン3及び低圧ピストン2を左方へ押し戻す。(4) Therefore, the pressure of the fuel introduced into the high pressure chamber 6 pushes the high pressure piston 3 and the low pressure piston 2 back to the left.
このとき低圧ピストン2がシリンダ4の端面に近づくと
、まず低圧ピストン2の頭部に設けられたパルプ12が
シリンダ4の端面に設けられた低圧油圧孔7を塞ぐ、低
圧油圧孔7が塞がれると、低圧室5内の燃料は逃げ通が
なくなるので低圧ピストン2本体の左方への移動は徐々
に減速される。At this time, when the low pressure piston 2 approaches the end face of the cylinder 4, the pulp 12 provided on the head of the low pressure piston 2 first blocks the low pressure hydraulic hole 7 provided on the end face of the cylinder 4. When this happens, the fuel in the low pressure chamber 5 cannot escape, so the leftward movement of the low pressure piston 2 body is gradually decelerated.
即ち、低圧室5内の圧力は低圧ピストン2の移動と共に
上昇し、低圧ピストン2を高圧ピストン3により押して
いる力と釣り合った位置で低圧ピストン2は停止する。That is, the pressure within the low pressure chamber 5 increases as the low pressure piston 2 moves, and the low pressure piston 2 stops at a position balanced with the force pushing the low pressure piston 2 by the high pressure piston 3.
この為、低圧ピストン2は徐々、に減速することが可能
でしかもシリンダ4の端面に衝突することがなくスムー
ズな運転が可能となる。その結果、噴射ノズル9が異常
噴射をしたり、低圧ピストン2がシリンダ4の端面に衝
突し油圧シリンダ1を破損したりすることがなくなる。Therefore, the low-pressure piston 2 can be gradually decelerated and can operate smoothly without colliding with the end face of the cylinder 4. As a result, the injection nozzle 9 will not perform abnormal injection, and the low-pressure piston 2 will not collide with the end face of the cylinder 4 and damage the hydraulic cylinder 1.
尚上述した実施例においては、パルプ12によ(5)
り低圧油圧孔7を完全に塞ぎ、低圧ピストン2を、シリ
ンダ4の端面に衝突させないようにしたが、低圧ピスト
ン2の位置をシリンダ4の端面まで引き戻したい場合に
は、第3図のように絞り18を設けるとよい。第3図で
は、パルプ12が低圧油圧孔7を塞いだ際に低圧室5と
低圧油圧孔7との間に細い絞りが構成されるようパルプ
12に絞り18を形成し、パルプ12がシリンダ4の端
面を塞いだ後、低圧ピストン2の速度を減速しながらシ
リンダ端面まで、動(ようにしている。In the above-mentioned embodiment, the low pressure hydraulic hole 7 was completely blocked by the pulp 12 (5) to prevent the low pressure piston 2 from colliding with the end face of the cylinder 4, but the position of the low pressure piston 2 was changed to If you want to pull it back to the end face, it is advisable to provide a diaphragm 18 as shown in FIG. In FIG. 3, a throttle 18 is formed in the pulp 12 so that a narrow throttle is formed between the low pressure chamber 5 and the low pressure hydraulic hole 7 when the pulp 12 closes the low pressure hydraulic hole 7, and the pulp 12 is inserted into the cylinder 4. After closing the end face of the cylinder, the low pressure piston 2 is moved to the end face of the cylinder while decelerating its speed.
また、上述の実施例においては、パルプ12を低圧ピス
トン2の頭部に設けたが、シリンダ4の端面にパルプ1
2を設けても同様の効果が得られる。Further, in the above embodiment, the pulp 12 was provided at the head of the low pressure piston 2, but the pulp 12 was provided at the end surface of the cylinder 4.
Even if 2 is provided, the same effect can be obtained.
以上説明した様に本発明ではビスレ1部もしくはシリン
ダ端面に油圧孔の少なくとも1部を塞ぐことの可能なパ
ルプを設はピストンが移動する際にはシリンダ端面に衝
突する以前に、該パルプが油圧孔の少な(とも一部を塞
ぐようにしたため、シリンダとピストンの間の圧力室の
圧力を上昇さく6)
せて、ピストンに加わる力と圧力室内の圧力がバランス
する位置にピストンを減速あるいは停止させ、シリンダ
への衝撃力を緩和することができる。As explained above, in the present invention, pulp capable of blocking at least part of the hydraulic holes is provided in one part of the screw thread or the end face of the cylinder, so that when the piston moves, the pulp is By reducing the number of holes (and partially blocking them, the pressure in the pressure chamber between the cylinder and piston increases6), the piston is decelerated or stopped at a position where the force applied to the piston and the pressure in the pressure chamber are balanced. It is possible to reduce the impact force on the cylinder.
そのため、ピストンがシリンダへ衝突した際に生じる反
力によってピストンがダンピングするのを避け、噴射ノ
ズルからの異常噴射等を避ける事が出来、スムーズな運
転が可能となるという、優れた効果を有している。Therefore, it has the excellent effect of avoiding damping of the piston due to the reaction force generated when the piston collides with the cylinder, preventing abnormal injection from the injection nozzle, and enabling smooth operation. ing.
第1図は従来の構成を示す断面図、第2図は本発明装置
の一実施例の構成を示す断面図、第3図は本発明装置の
他の例を示す断面図である。
1・・・油圧シリンダ、2・・・低圧ピストン、3・・
・高圧ピストン、4・・・シリンダ、5・・・低圧室、
7・・・低圧油圧孔、12・・・パルプ。
代理人弁理士 岡 部 隆
(7)
手続補正書(方式)
昭和57年特許■第48406号
2発明の名称
油圧シリンダ装置
3補正をする者
事件との関係 特許出願人
愛知県西尾市下羽角町岩谷14番地
(469)株式会社 日本自動車部品総合研究所代表者
三田省吾
4代 理 人
〒448 愛知県刈谷市昭和町1丁目1番地5 補正
命令の日付
な説明」に訂正します。FIG. 1 is a cross-sectional view showing a conventional configuration, FIG. 2 is a cross-sectional view showing the configuration of one embodiment of the device of the present invention, and FIG. 3 is a cross-sectional view showing another example of the device of the present invention. 1...Hydraulic cylinder, 2...Low pressure piston, 3...
・High pressure piston, 4... cylinder, 5... low pressure chamber,
7...Low pressure hydraulic hole, 12...Pulp. Representative Patent Attorney Takashi Okabe (7) Procedural amendment (method) 1982 Patent No. 48406 2 Name of the invention Hydraulic cylinder device 3 Person making the amendment Relationship to the case Patent applicant Iwatani, Shimohazuno-cho, Nishio City, Aichi Prefecture Address 14 (469) Japan Auto Parts Research Institute Co., Ltd. Representative Shogo Mita 4th Director Mr. 1-1-5 Showa-cho, Kariya-shi, Aichi Prefecture 448 The date and explanation of the amendment order has been corrected.
Claims (1)
動をするピストンとを備え、前記シリンダ端面に流体導
入・導出用の油圧孔を形成した油圧シリンダ装置におい
て、前記ピストン頭部もしくは前記シリンダ端面&:前
記油圧孔の少なくとも一部を閉塞可能なパルプを設け、
前記ピストンが、前記シリンダ端面に当接する以前にこ
のパルプが前記油圧孔の少なくとも1部を塞ぐことを特
徴とした油圧シリンダ代↑。 (2、特許請求の範囲第1項記載の油圧シリンダ装置に
おいて、前記パルプが油圧孔を塞いだ際前記シリンダ端
面との前記油圧孔との間絞りが構成されることを特徴と
した油圧シリンダ装置。(1) A hydraulic cylinder device comprising a cylinder and a piston that reciprocates within the cylinder by hydraulic pressure, and in which a hydraulic hole for introducing and discharging fluid is formed in the end face of the cylinder, in which the piston head or the cylinder end face & : Providing a pulp capable of blocking at least a portion of the hydraulic hole,
The hydraulic cylinder gap ↑ is characterized in that the pulp blocks at least a portion of the hydraulic hole before the piston comes into contact with the cylinder end surface. (2. The hydraulic cylinder device according to claim 1, wherein when the pulp closes the hydraulic hole, a restriction is formed between the cylinder end face and the hydraulic hole. .
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4840682A JPS58166106A (en) | 1982-03-25 | 1982-03-25 | Hydraulic cylinder device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP4840682A JPS58166106A (en) | 1982-03-25 | 1982-03-25 | Hydraulic cylinder device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS58166106A true JPS58166106A (en) | 1983-10-01 |
Family
ID=12802418
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP4840682A Pending JPS58166106A (en) | 1982-03-25 | 1982-03-25 | Hydraulic cylinder device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS58166106A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4649398A (en) * | 1984-01-25 | 1987-03-10 | Nippondenso Co., Ltd. | Motor driven extensible rod antenna for vehicles with position control circuit |
US7739941B2 (en) | 2004-08-27 | 2010-06-22 | Westport Power Inc. | Hydraulic drive system and method of operating a hydraulic drive system |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5531338A (en) * | 1978-08-28 | 1980-03-05 | Fujitsu Ltd | Automatic equalization system |
-
1982
- 1982-03-25 JP JP4840682A patent/JPS58166106A/en active Pending
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5531338A (en) * | 1978-08-28 | 1980-03-05 | Fujitsu Ltd | Automatic equalization system |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4649398A (en) * | 1984-01-25 | 1987-03-10 | Nippondenso Co., Ltd. | Motor driven extensible rod antenna for vehicles with position control circuit |
US7739941B2 (en) | 2004-08-27 | 2010-06-22 | Westport Power Inc. | Hydraulic drive system and method of operating a hydraulic drive system |
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