JPH03229082A - Electrohydraulic torque generator - Google Patents
Electrohydraulic torque generatorInfo
- Publication number
- JPH03229082A JPH03229082A JP2302790A JP2302790A JPH03229082A JP H03229082 A JPH03229082 A JP H03229082A JP 2302790 A JP2302790 A JP 2302790A JP 2302790 A JP2302790 A JP 2302790A JP H03229082 A JPH03229082 A JP H03229082A
- Authority
- JP
- Japan
- Prior art keywords
- hydraulic
- valve
- hydraulic pump
- motor
- individual
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 3
- 239000010720 hydraulic oil Substances 0.000 description 2
- 239000000446 fuel Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Landscapes
- Fluid-Driven Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、船舶のバラストライン、ビルジライン、燃料
ライン及び消火ライン等のバルブのリモートコントロー
ルシスチムニ関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Application Field] The present invention relates to a remote control system for valves such as ballast lines, bilge lines, fuel lines and fire lines of ships.
従来の船舶のバルブのリモートコントロールシステムの
基本回路図ン、第8図に示す。A basic circuit diagram of a conventional remote control system for ship valves is shown in FIG.
バルブ(8]Jとしては、ボール弁、王形弁又にバタフ
ライ弁等が使用さn、その駆動用アクチュエータとして
は油圧式揺動モータが使用さnるoバルブ(81)ト[
動モータ(82〕の組立図ン第7図に示す。従来はこの
バルブと揺動モータンセットしたもの馨船内各所(S常
50〜300個所)に配置し、その動力源としての油圧
ポンプユニッ)(84)及び電磁弁スタンド(83)Y
1ケ所に配置する方式が採用きれている。A ball valve, a king valve, a butterfly valve, etc. is used as the valve (8), and a hydraulic swing motor is used as the actuator for driving the valve (81).
The assembly diagram of the swing motor (82) is shown in Figure 7. Conventionally, this valve and swing motor set were placed in various locations on the ship (usually 50 to 300 locations), and a hydraulic pump unit was used as the power source. 84) and solenoid valve stand (83)Y
The method of placing it in one place has been successfully adopted.
従来の船舶のバルブのリモートコントロールシステムに
あっては、fi内各所(通常50〜3001固所)に配
置されたバルブ(81)に設置された揺動モータ(82
)と電磁弁スタンド(83)との間の油圧配管の本数が
多く美大な費用と時間ケ要するという問題点があった。In a conventional remote control system for a valve on a ship, a swing motor (82
) and the solenoid valve stand (83), which requires a large amount of cost and time.
又油圧ボンプユニン)(84)は、50〜3 (10個
のバルブ(8I〕のパワー乞まかなう必要が生じ、装置
が大形化し船内スペースを取りかつ騒音が大きくなると
いう問題点があった。In addition, the hydraulic pump unit (84) had the problem that it was necessary to supply the power of 50 to 10 valves (8I), making the device large, taking up space inside the ship, and increasing noise.
本発明は、船舶のバルブのリモートコントロールシステ
ムにおいて、船内油圧配管が不要で。The present invention is a remote control system for ship valves that eliminates the need for onboard hydraulic piping.
かつ低騒音の電動油圧トルク発生装置χ得ること?目的
としている。And get a low-noise electro-hydraulic torque generator χ? The purpose is
上記目的を達成するために9本発明の電動油圧トルク発
生装置においては、第1図に示す基本油圧回路Y採用し
、1個のバルブ〔]〕につきそnぞれ】個の電動機(4
)と油圧ポンプ(5)ン設直した揺動モータ(2)Yバ
ルブ(])に取りつけることにした。In order to achieve the above object, the electro-hydraulic torque generator of the present invention adopts the basic hydraulic circuit Y shown in FIG.
) and the hydraulic pump (5) and the reinstalled swing motor (2) Y valve (]).
又、バルブの開閉方図制御用の電磁弁とじてに、もれの
多いスプールタイプをやめポペット形電磁弁(3)ン採
用し、油タンクに、油圧ポンプ(5)の収入性能アップ
及び不装置の取り付は方向馨全方同可能とするため加圧
タンク(7)χ採用した。In addition, for the solenoid valve for controlling the opening/closing direction of the valve, we have replaced the spool type, which tends to leak, with a poppet type solenoid valve (3), which improves the revenue performance of the hydraulic pump (5) and improves the efficiency of the oil tank. A pressurized tank (7) was used to install the device in all directions.
上記のように構成された電動油圧トルク発生装*におい
てに、】個のバルブ(1)に各々1個の電動機(4)、
油圧ポンプ(5)及び油圧機6乞セットして組込んでい
るため、船内油圧配管工事は不要となる。In the electro-hydraulic torque generating device* configured as above, one electric motor (4) is provided for each of the ] valves (1),
Since the hydraulic pump (5) and hydraulic machine 6 are installed as a set, there is no need for onboard hydraulic piping work.
又、1個のバルブ(])駆動用の小さい油圧源を個々の
バルブに塔載することになるため、騒音は極めて小さく
なる。しかもポペット形電磁弁(3)及び加圧タンク(
7)の採用によるシステム効率アップにより、油圧源の
パワーχ小さく押えることができる。Further, since a small hydraulic power source for driving one valve () is mounted on each valve, noise is extremely reduced. Moreover, the poppet type solenoid valve (3) and the pressurized tank (
By increasing system efficiency by adopting 7), the power χ of the hydraulic power source can be kept small.
実施例について図面ケ参照して説明すると。 An example will be explained with reference to the drawings.
第1図に基本油圧回路図χ示す。第2図に正面図を示す
02階建起置とし1階部に電動機(4)。Fig. 1 shows a basic hydraulic circuit diagram. The front view is shown in Figure 2.It is a two-story building with an electric motor (4) on the first floor.
油圧ポンプ(5)、リリーフ弁(6)、加圧タンク(7
)及び揺動モータ(2ノン配置し2階部にポペット形電
磁弁(3)及び付属品ン設置する。Hydraulic pump (5), relief valve (6), pressurized tank (7)
) and swing motor (2), and a poppet type solenoid valve (3) and accessories will be installed on the second floor.
第3図に第2区のA−A断面図χ示す。揺動モータ(2
)としては9機械効率の最も艮いラックアンドビニオン
タイプの揺動モータ暑採用。FIG. 3 shows a sectional view χ taken along the line AA of the second section. Swing motor (2
) Adopts a rack-and-binion type swing motor with the highest mechanical efficiency.
油圧ポンプ(5)にはピストンポンプを設置する。A piston pump is installed as the hydraulic pump (5).
第4図に第3図のB−BI!IT面図を示す。第5図に
第2図のC−C矢視図χ示す。第6図に第3図のD−D
IFi面図Y示す。加圧タンク(7)には。Figure 4 shows B-BI in Figure 3! An IT diagram is shown. FIG. 5 shows a view taken along the line C--C in FIG. 2. Figure 6 shows D-D in Figure 3.
IFi plane view Y is shown. In the pressurized tank (7).
加圧シリンダ(9)を取ジつけ、タンク内の作動油は約
0.5kf/−位に常時加圧する方式ン採用するO
本発明の電動油圧トルク発生装置の大きさは。A pressurizing cylinder (9) is attached, and the hydraulic oil in the tank is constantly pressurized to approximately 0.5 kf/-.
トルク150kfmクラスで縦26α慣26m高さ29
m、l量55kf位となり、従来のトルク発生装置に比
べ半分以下の重重、スペースでまとめることができる。Torque 150kfm class, length 26α customization 26m height 29
The torque generation device has an amount of about 55 kf, and can be assembled in less than half the weight and space compared to conventional torque generators.
本発明は9以上説明したように構成されているので、以
下に記載されているような効果を奏する。Since the present invention is configured as described above, it produces the effects described below.
1個のバルブ毎に油圧システムがバックージさnている
ため、従来美大な工数?要していた船内油圧配管工事が
不要となる。又、油圧ポンプユニット(84J及び電磁
弁スタンド(83)等の大きい油圧装置の設置の必要が
なく、船内スペースの確保にわずられされることも無く
なる。Because the hydraulic system is backed up for each valve, it takes an enormous amount of man-hours compared to before. This eliminates the need for onboard hydraulic piping work. Furthermore, there is no need to install large hydraulic devices such as a hydraulic pump unit (84J) and a solenoid valve stand (83), and there is no need to worry about securing space inside the ship.
更に1個のバルブ毎に油圧システム?構成するので油圧
源のパワーが小さくてすむため、極めて騒音の低いシス
テムを得ることができる。And a hydraulic system for each valve? Because of this structure, the power of the hydraulic power source can be small, making it possible to obtain a system with extremely low noise.
又、加圧タンク(7)ン採用しているため、いかなる方
向に本装置乞取り付けても、油圧ポンプ(5)へは作動
油がチャージ嘔れてシステムが正常に作動するため、全
ての方向に取シ付けが可能となる。In addition, since the pressurized tank (7) is used, no matter which direction this device is installed, the hydraulic pump (5) will be charged with hydraulic oil and the system will operate normally. It is possible to install it on the
第1図は本発明に係る基本油圧回路図、第2図は正面図
、第3図は第2図のA−A断面図。
第4図に第3図のB−B断面図、第5図は第2図のC−
C矢視図、第6図は第3図のD−D断面図、第7図は従
来品のバルブと揺動モータの組立図、第8図は従来シス
テムの基本回路図である。
工・・・・・・・・・バルブ
2・・・・・・・・・ポペット形電磁弁5・・・・・・
・・・油圧ポンプ
7・・・・・・・・・加圧タンク
9・・・・・・・・・加圧シリンダ
81・・・・・・・・・バルブ
2・・・・・・・・・揺動モータ
4・・・・・・・・・電動機
6・・・・・・・・・リリーフ弁
8・・・・・・・・・端子箱
82・・・・・・・・・揺動モータ
83・・・・・・・・・電磁弁スタンド84・・・・・
・・・油圧ボンフ
ユニツ
トFIG. 1 is a basic hydraulic circuit diagram according to the present invention, FIG. 2 is a front view, and FIG. 3 is a sectional view taken along line AA in FIG. 2. Figure 4 is a sectional view taken along line B-B in Figure 3, and Figure 5 is a cross-sectional view taken along line C-- in Figure 2.
6 is a sectional view taken along line DD in FIG. 3, FIG. 7 is an assembly diagram of a conventional valve and swing motor, and FIG. 8 is a basic circuit diagram of a conventional system. Engineering... Valve 2... Poppet type solenoid valve 5...
・・・Hydraulic pump 7・・・・・・Pressure tank 9・・・・・・Pressure cylinder 81・・・・・・・・・Valve 2・・・・・・・・・...Rolling motor 4...Electric motor 6...Relief valve 8...Terminal box 82... Swing motor 83... Solenoid valve stand 84...
・・・Hydraulic bomb unit
Claims (1)
機(4)、油圧ポンプ(5)、リリーフ弁(6)及び加
工タンク(7)を取りつけた電動油圧トルク発生装置1. Electric hydraulic torque generator equipped with a swing motor (2), poppet type solenoid valve (3), electric motor (4), hydraulic pump (5), relief valve (6) and processing tank (7)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2023027A JP2614128B2 (en) | 1990-02-01 | 1990-02-01 | Ship hydraulic valve control system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2023027A JP2614128B2 (en) | 1990-02-01 | 1990-02-01 | Ship hydraulic valve control system |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH03229082A true JPH03229082A (en) | 1991-10-11 |
JP2614128B2 JP2614128B2 (en) | 1997-05-28 |
Family
ID=12098992
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2023027A Expired - Lifetime JP2614128B2 (en) | 1990-02-01 | 1990-02-01 | Ship hydraulic valve control system |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2614128B2 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004156785A (en) * | 2002-11-07 | 2004-06-03 | Ksb Sas | Control device for integrated electrohydraulic actuator |
JP2004169914A (en) * | 2002-11-07 | 2004-06-17 | Ksb Sas | Cock fitting system used in ship |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6535360B2 (en) * | 2017-04-13 | 2019-06-26 | 株式会社シー・オー・シー | Ship valve control system |
JP6448740B1 (en) * | 2017-10-13 | 2019-01-09 | 株式会社シー・オー・シー | Ship valve control system |
CN107740747A (en) * | 2017-10-13 | 2018-02-27 | 三汽车起重机械有限公司 | The control method of speed limit hydraulic motor, crane and motor rotary speed |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5372222A (en) * | 1976-12-09 | 1978-06-27 | United Technologies Corp | Operating system for use in liquid pressure operating valve |
JPS6023373U (en) * | 1983-07-26 | 1985-02-18 | 三菱重工業株式会社 | valve remote control device |
-
1990
- 1990-02-01 JP JP2023027A patent/JP2614128B2/en not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5372222A (en) * | 1976-12-09 | 1978-06-27 | United Technologies Corp | Operating system for use in liquid pressure operating valve |
JPS6023373U (en) * | 1983-07-26 | 1985-02-18 | 三菱重工業株式会社 | valve remote control device |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004156785A (en) * | 2002-11-07 | 2004-06-03 | Ksb Sas | Control device for integrated electrohydraulic actuator |
JP2004169914A (en) * | 2002-11-07 | 2004-06-17 | Ksb Sas | Cock fitting system used in ship |
JP4589616B2 (en) * | 2002-11-07 | 2010-12-01 | カー エス ベー エス.アー.エス. | Integrated electro-hydraulic actuator controller |
Also Published As
Publication number | Publication date |
---|---|
JP2614128B2 (en) | 1997-05-28 |
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