JPS6280302A - Closed circuit electro-hydraulic actuator package - Google Patents
Closed circuit electro-hydraulic actuator packageInfo
- Publication number
- JPS6280302A JPS6280302A JP21767685A JP21767685A JPS6280302A JP S6280302 A JPS6280302 A JP S6280302A JP 21767685 A JP21767685 A JP 21767685A JP 21767685 A JP21767685 A JP 21767685A JP S6280302 A JPS6280302 A JP S6280302A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- actuator
- chamber
- hydraulic
- accumulator
- 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
Landscapes
- Servomotors (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は閉回路電気油圧アクチュエータパッケージに係
り、特に航空機用操縦系統の舵面制御アクチュエータ等
に適用できる他、一般産業機器やロボット等のパワーパ
ッケージにも適用できる閉回路電気油圧アクチュエータ
パッケージに関する。[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a closed-circuit electro-hydraulic actuator package, and is particularly applicable to control surface control actuators for aircraft flight control systems, as well as power applications for general industrial equipment, robots, etc. The present invention relates to a closed circuit electro-hydraulic actuator package that can also be applied to a package.
従来の電気油圧アクチュエータパッケージの回路構成は
第４図に示すようになっている。すなわち、直流サーボ
モータ１により駆動される可逆式油圧ポンプ２を設け、
このポンプ２をアクチュエータ本体３に油路４Ａ、４Ｂ
を介して接続している。アクチュエータ本体３はシリン
ダ５内にピストン６を内蔵して一対の油圧室７Ａ、７Ｂ
を区画形成し、ピストン６と一体になった作動ロッド８
を油圧室７Ａ、７Ｂの圧力差によって往復駆動させるよ
うにしている。このため、ポンプ２の正回転時の吐出側
ポートを第１油路４Ａを介して一方の油圧室７Ａに接続
し、逆回転時の吐出側ポートを第２油路４Ｂを介して他
方の油圧室７Ｂに接続して閉回路を構成させている。ま
た、第１．第２油路４Ａ、４Ｂに初期圧力を導入してア
クチュエ−夕中立時の剛性を保持するために、アキュム
レータ９が設けられている。アキュムレータ９はピスト
ン１０により油室１１とガス室１２に区画し。The circuit configuration of a conventional electro-hydraulic actuator package is shown in FIG. That is, a reversible hydraulic pump 2 driven by a DC servo motor 1 is provided,
This pump 2 is connected to the actuator body 3 through oil passages 4A and 4B.
are connected via. The actuator body 3 has a piston 6 built into the cylinder 5 and has a pair of hydraulic chambers 7A and 7B.
an actuating rod 8 which is integrally formed with the piston 6;
is driven back and forth by the pressure difference between the hydraulic chambers 7A and 7B. For this reason, the discharge side port of the pump 2 during forward rotation is connected to one hydraulic chamber 7A via the first oil passage 4A, and the discharge side port during reverse rotation is connected to the other hydraulic pressure chamber 7A via the second oil passage 4B. It is connected to chamber 7B to form a closed circuit. Also, 1st. An accumulator 9 is provided to introduce initial pressure into the second oil passages 4A, 4B to maintain rigidity when the actuator is in neutral position. The accumulator 9 is divided into an oil chamber 11 and a gas chamber 12 by a piston 10.
ガス室１２内にガスを封入したもので、油室１１に前記
第１．第２油路４Ａ、４Ｂの回路圧を導いている。第１
、第２油路４Ａ、４Ｂと油室１１との接続のため、油室
１１に開口する主導入油路１３を分岐し、一方の分岐第
１油路１３Ａを第１油路４Ａに連通させ、他方の分岐第
２油路１３Ｂを第２油路４Ｂに連通させている。そして
、分岐油路１２Ａ、１３Ｂにはチェックバルブ１４Ａ、
１４Ｂを介装し、高圧側（ポンプ吐出側）の回路圧がア
キュムレータ９側に作用しないようにしている。The gas chamber 12 is filled with gas, and the oil chamber 11 is filled with gas. It guides the circuit pressure of the second oil passages 4A and 4B. 1st
In order to connect the second oil passages 4A, 4B and the oil chamber 11, the main introduction oil passage 13 that opens into the oil chamber 11 is branched, and one branched first oil passage 13A is communicated with the first oil passage 4A. , the other branched second oil passage 13B is communicated with the second oil passage 4B. And check valves 14A,
14B is interposed to prevent circuit pressure on the high pressure side (pump discharge side) from acting on the accumulator 9 side.
したがって、ポンプ２の正転時には第１油路４Ａ側がポ
ンプ吐出圧となってアクチュエータ本体３の一方の油圧
室７Ａに作用し、他方の油圧室７Ｂには第２油路４Ｂを
通じてアキュムレータ９のガス室１２内圧力が作用する
ので、アクチュエータ本体３の作動ロッド８は油圧室７
Ａ、７Ｂの圧力差（ポンプ吐出圧とガス圧の差）によっ
て正方向に移動し、舵面制御をなすことができる。Therefore, when the pump 2 rotates normally, the first oil passage 4A side becomes the pump discharge pressure and acts on one hydraulic chamber 7A of the actuator body 3, and the other hydraulic chamber 7B is supplied with the gas of the accumulator 9 through the second oil passage 4B. Since the pressure inside the chamber 12 acts, the actuating rod 8 of the actuator body 3 is moved into the hydraulic chamber 7.
The pressure difference between A and 7B (the difference between the pump discharge pressure and the gas pressure) allows the control surface to be controlled by moving in the forward direction.
なお、ポンプ２のケース内にはアキュムレータ９の設定
圧が作用して低圧保持をなすように、アキュムレータ油
室１１との接続油路１５を開口させている。また、直流
サーボモータ１への駆動信号は増幅器１６、コントロー
ラ１７を通して入力するようにし、アクチュエータ本体
９に設けた位置変位検出器１８からの検出信号を増幅器
１６を通じてコントローラ１７に入力させて位置補正を
なすように構成している。図中１９はモータ１に付属し
たタコジェネレータ、２０Ａ、２０Ｂは回路保護用リリ
ーフバルブである。Note that an oil passage 15 connecting to the accumulator oil chamber 11 is opened so that the set pressure of the accumulator 9 acts inside the case of the pump 2 to maintain a low pressure. Further, a drive signal to the DC servo motor 1 is inputted through an amplifier 16 and a controller 17, and a detection signal from a position displacement detector 18 provided in the actuator body 9 is inputted to the controller 17 through the amplifier 16 to perform position correction. It is configured as follows. In the figure, 19 is a tacho generator attached to the motor 1, and 20A and 20B are circuit protection relief valves.
ところが、従来の閉回路電気油圧アクチュエータパッケ
ージでは、アクチュエータ本体のピストン前後の有効差
圧を大きくとれず、かつアクチュエータ本体の片側のみ
の圧力制御であるため、アクチュエータ本体としての剛
性が小さい問題があった。すなわち、従来構成における
圧力特性は、第５図に示されるようになっており、アク
チュエータ本体の非作動時にはアキュムレータ９のガス
圧が第１．第２油路４Ａ、４Ｂに一定の初期圧力Ｐａと
して作用している。いま、中立位置（入力「０」）から
ポンプ２を正回転すると、第１油路４Ａの内圧はポンプ
吐出圧となって、第５回実線Ａのように立上がる。この
圧力と初期圧力Ｐｏとの差圧が７クチユ工−タ本体３の
駆動圧力となる有効差圧である。ポンプ２の逆回転時は
同図破線Ｂのようになり、やはり初期圧力Ｐｏとの差が
有効差圧となるのである。したがって、有効差圧を大き
くするためには初期圧力を下げるかポンプ２の能力を大
きくしなければならないが、初期圧力を低下するとアク
チュエータ本体３の外力による剛性を保持し得す、ポン
プ能力の増大は大型化。However, with conventional closed-circuit electro-hydraulic actuator packages, it is not possible to maintain a large effective differential pressure across the piston of the actuator body, and the pressure is controlled only on one side of the actuator body, so the rigidity of the actuator body is low. . That is, the pressure characteristics in the conventional configuration are as shown in FIG. A constant initial pressure Pa acts on the second oil passages 4A and 4B. Now, when the pump 2 is rotated forward from the neutral position (input "0"), the internal pressure of the first oil passage 4A becomes the pump discharge pressure and rises as shown by the fifth solid line A. The differential pressure between this pressure and the initial pressure Po is the effective differential pressure that becomes the driving pressure for the seven-cut machine main body 3. When the pump 2 rotates in the reverse direction, it becomes as shown by the broken line B in the figure, and the difference from the initial pressure Po becomes the effective differential pressure. Therefore, in order to increase the effective differential pressure, it is necessary to lower the initial pressure or increase the capacity of the pump 2, but if the initial pressure is lowered, the rigidity of the actuator body 3 due to external force can be maintained, and the pump capacity increases. is larger.
重量増を招く問題がある。There is a problem of increased weight.
本発明は、上記従来の問題点に着目し、アクチュエータ
剛性を向上し、有効差圧を大きくできる小型の閉回路電
気油圧アクチュエータパッケージを提供することを目的
とする。The present invention has focused on the above-mentioned conventional problems, and an object of the present invention is to provide a small-sized closed-circuit electro-hydraulic actuator package that can improve actuator rigidity and increase effective differential pressure.
〔問題点を解決するための手段および作用〕上記目的を
達成するために、本発明に係る閉回路電気油圧アクチュ
エータパッケージは、電動モータにより駆動される可逆
ポンプの吸排口とアクチュエータ本体の各油圧室とを接
続して閉回路を構成する油路を通じて回路圧が導入され
る油室と、ガスが封入されたガス室とを備えたアキュム
レータに対し、前記油室を共通ピストンにより２分割し
各分割室の各々に前記アクチュエータの各油圧室への回
路圧を導入させるように構成したものである。そして、
アクチュエータにより作動される機構に応じて１分割室
に受圧面積を互いに等しくし、あるいは面積差を与える
ようにして、適当な ゛作動特性を得るようにす
ればよい。[Means and effects for solving the problems] In order to achieve the above object, the closed circuit electro-hydraulic actuator package according to the present invention has the following advantages: For an accumulator, the oil chamber is divided into two by a common piston, and each division is divided into two by a common piston. The circuit pressure to each hydraulic chamber of the actuator is introduced into each of the chambers. and,
Depending on the mechanism operated by the actuator, the pressure-receiving area of each divided chamber may be made equal to each other or may be given a difference in area to obtain appropriate operating characteristics.
斯かる構成により、ポンプの駆動により一方のアクチュ
エータ油圧室に通じる油路圧が高まると。With such a configuration, when the pump is driven, the pressure in the oil passage leading to one of the actuator hydraulic chambers increases.
この回路圧が導入されるアキュムレータ内分割室内圧が
高圧となる。しかし、他方の吸入側油路が通じているア
キュムレータ内分割室は共通ピストンで仕切られている
ため、アキュムレータ内の圧力バランスにより他方の分
割油室内の増圧分だけ減圧し、当該アキュムレータ分割
室内圧が初期圧力より低下し、アクチュエータの排出側
油圧室も低下するのである。このようなことから、アク
チュエータピストン前後の差圧は初期圧力を起点として
増大するポンプ吐出圧と初期圧力から減少する圧力との
差圧となり、有効差圧を大きくとることができるのであ
る。The pressure in the divided chamber within the accumulator into which this circuit pressure is introduced becomes high pressure. However, since the divided chamber in the accumulator that the other suction side oil passage communicates with is partitioned by a common piston, the pressure in the accumulator is reduced by the increased pressure in the other divided oil chamber due to the pressure balance in the accumulator, and the pressure in the accumulator divided chamber is reduced by the increased pressure in the other divided oil chamber. is lower than the initial pressure, and the discharge side hydraulic chamber of the actuator is also lowered. For this reason, the differential pressure before and after the actuator piston is the differential pressure between the pump discharge pressure, which increases starting from the initial pressure, and the pressure, which decreases from the initial pressure, and it is possible to obtain a large effective differential pressure.
以下に、本発明に係る閉回路電気油圧アクチュエータの
実施例を第１〜３図を参照して詳細に説明する。 第１
図は実施例の閉回路電気油圧アクチュエータパッケージ
の回路構成図である。このアクチュエータパワーパッケ
ージは増幅器３０、コントローラ３１を通じて駆動指令
信号が入力する直流サーボモータ３２を備え、該モータ
３２を駆動源として定吐出型の可逆油圧ポンプ３３を回
転させるようにしている。ポンプ３３は２つの吸排口を
持ち、両眼排口を作動主体となるアクチュエータ本体３
４に接続している。アクチュエータ本体３４はピストン
３５により区画される２つの油圧室３６Ａ、３６Ｂを有
し、その一方の油圧室３６Ａにはポンプ３３の正回転時
に吐出側となる吸排口を第１油路３７Ａによって接続し
、他方の油圧室３６Ｂには逆転時に吐出側となる吸排口
を第２油路３７Ｂによって接続し、ポンプ３３との間で
閉回路を構成している。したがってポンプ３３の作動に
より、アクチュエータ本体３３のピストン３５前後に圧
力差が生じることで、アクチュエータピストン３５と一
体になった作動ロッド３８を往復移動させることができ
る。Embodiments of the closed circuit electro-hydraulic actuator according to the present invention will be described in detail below with reference to FIGS. 1 to 3. 1st
The figure is a circuit configuration diagram of a closed circuit electro-hydraulic actuator package according to an embodiment. This actuator power package includes an amplifier 30 and a DC servo motor 32 to which a drive command signal is input through a controller 31, and uses the motor 32 as a drive source to rotate a constant discharge type reversible hydraulic pump 33. The pump 33 has two suction and discharge ports, and the binocular discharge ports are connected to the actuator body 3 which is the main actuator.
Connected to 4. The actuator main body 34 has two hydraulic chambers 36A and 36B partitioned by a piston 35, and a suction/discharge port that becomes a discharge side when the pump 33 rotates forward is connected to one of the hydraulic chambers 36A by a first oil passage 37A. The other hydraulic chamber 36B is connected to a suction/discharge port which becomes a discharge side at the time of reverse rotation by a second oil passage 37B, and forms a closed circuit with the pump 33. Therefore, the operation of the pump 33 creates a pressure difference before and after the piston 35 of the actuator body 33, so that the actuating rod 38 integrated with the actuator piston 35 can be moved back and forth.
ここで、回路圧を一定に保持してアクチュエータ剛性を
維持するために設けられるアキュムレータ４０は次のよ
うに構成されている。すなわち、第２図に具体的構造を
示したように、このアキュムレータは円筒のシリ ゛ケ
ース４１を有し、その両端開口をカバー４２．４３によ
り閉塞して密閉容器としている。シリンダケース４１内
にはガス室４４と油室４５を区画するピストン４６が摺
動可能に装着されているが、油室４５は更に２つの室４
５Ａ、４５Ｂに分割されている。このため前記ピストン
４６は一端開口の円筒容器状に形成され、開口部内にカ
バー４２から突出された油室分割ロッド４７を挿入させ
ている。そして、ロッド４７の先端で閉塞されるピスト
ン４６の内部空間を第１分割油室４５Ａとし、ロッド４
７の外周部に形成される空間を第２分割油室４５Ｂとし
ているものである。もちろん、ピストン４６とシリンダ
ケース４１との摺動部、ピストン４６とロッド４７との
摺動部等にはシール４８を取付け、流体の漏れがないよ
うにしている。このように内部を３室を形成したアキュ
ムレータ４０には、初期回路圧を導入するためにガス室
４４にガスを封入し、両油室４５Ａ、４５Ｂには作動油
を充填するようにしている。このため、ガス室４４に開
口するガス封入ポート４９をカバー４３に形成し、封入
後にガスバルブ５０を遮断するようにして封入圧力を初
期圧力として設定するようにしている。Here, the accumulator 40, which is provided to keep the circuit pressure constant and maintain the actuator rigidity, is configured as follows. That is, as the specific structure is shown in FIG. 2, this accumulator has a cylindrical case 41, and both openings of the accumulator are closed with covers 42 and 43 to form a closed container. A piston 46 that partitions a gas chamber 44 and an oil chamber 45 is slidably mounted inside the cylinder case 41.
It is divided into 5A and 45B. For this purpose, the piston 46 is formed in the shape of a cylindrical container with one end open, and an oil chamber dividing rod 47 protruding from the cover 42 is inserted into the opening. The inner space of the piston 46 that is closed at the tip of the rod 47 is defined as a first divided oil chamber 45A, and the rod 4
The space formed at the outer circumferential portion of 7 is the second divided oil chamber 45B. Of course, seals 48 are attached to the sliding parts between the piston 46 and the cylinder case 41, the sliding parts between the piston 46 and the rod 47, etc., to prevent fluid leakage. In the accumulator 40, which has three internal chambers, the gas chamber 44 is filled with gas to introduce the initial circuit pressure, and both oil chambers 45A and 45B are filled with hydraulic oil. For this reason, a gas filling port 49 that opens into the gas chamber 44 is formed in the cover 43, and after filling, the gas valve 50 is shut off to set the filling pressure as the initial pressure.
また、第１分割油室４５Ａに通じる第１ポート５１をロ
ッド４７に形成し、第２分割油室４５Ｂに通じる第２ボ
ート５２をカバー４２に形成している。Further, a first port 51 communicating with the first divided oil chamber 45A is formed in the rod 47, and a second boat 52 communicating with the second divided oil chamber 45B is formed in the cover 42.
更にこの実施例では第１．第２分割油室４５Ａ。Furthermore, in this embodiment, the first. Second divided oil chamber 45A.
４５Ｂの受圧面積がガス室４４の受圧面積の１７２とな
るように、ピストン４６の各室に対面する面積を調整し
ている。これは具体的にはピストン４６のロッド挿入開
口面積を調整することで簡単に設定できる。The area of the piston 46 facing each chamber is adjusted so that the pressure receiving area of the piston 45B is 172 times the pressure receiving area of the gas chamber 44. Specifically, this can be easily set by adjusting the rod insertion opening area of the piston 46.
このようなアキュムレータ４ｏを前記閉回路と接続する
わけであるが、これは、前記第１油路３７Ａから分岐さ
れた第１分岐油路５３Ａをアキュムレータ４０の第１ポ
ート５１に接続し、また第２油路３７Ｂから分岐された
第２分岐油路５３Ｂを第２ポート５２に接続するように
して、ポンプ３３の正転時吐出側回路圧力を第１分割油
室４５Ａに導入するようにするとともに逆転時の吐出側
回路圧力を第２分割油室４５Ｂに導入するようにしてい
る。Such an accumulator 4o is connected to the closed circuit by connecting the first branch oil passage 53A branched from the first oil passage 37A to the first port 51 of the accumulator 40, and also connecting the first branch oil passage 53A branched from the first oil passage 37A to the first port 51 of the accumulator 40. A second branch oil passage 53B branched from the second oil passage 37B is connected to the second port 52, so that the discharge side circuit pressure during normal rotation of the pump 33 is introduced into the first divided oil chamber 45A. The discharge side circuit pressure during reverse rotation is introduced into the second divided oil chamber 45B.
また、前記第１、第２分岐油路５３Ａ、５３Ｂ間にポン
プ３３のケース内との接続油路５４と接続される油路５
５が設けられ、該油路５５は逆止弁５６Ａ、５６Ｂを介
在させている。逆止弁５６Ａ、５６Ｂはポンプ吐出圧と
なる高圧側を遮断し、゛ポンプ吸入圧となる低圧の回路
圧がポンプケースに作用するようにその方向が設定され
ている。Also, an oil passage 5 connected to a connecting oil passage 54 to the inside of the case of the pump 33 between the first and second branch oil passages 53A and 53B.
5 is provided, and the oil passage 55 has check valves 56A and 56B interposed therebetween. The check valves 56A and 56B are oriented in such a way that the high pressure side, which is the pump discharge pressure, is shut off, and the low circuit pressure, which is the pump suction pressure, acts on the pump case.
なお、第１油路３７Ａと第２油路３７Ｂには回路保護の
ためのリリーフバルブ５７Ａ、５７Ｂが各々バイパス路
５８Ａ、５８Ｂ中に介装され、更に当該アクチュエータ
回路システムに故障が生じた場合に、アクチュエータ本
体３４の抵抗軽減のために常閉バイパスバルブ５９を別
のバイパス路６０に介装させている。また、前記直流サ
ーボモータ３２にはタコジェネレータ等の回転数検出器
６１が取付けられ、モータ回転数をモニタし、コントロ
ーラ３１にフィードバックして回転数補正機能をもたせ
ており、更に、アクチュエータ本体３４にはピストン位
置検出器６２を取付け、検出値を増幅器３０にフィード
バックして位置補正を行わせるようにしている。In addition, relief valves 57A and 57B for circuit protection are interposed in bypass paths 58A and 58B, respectively, in the first oil passage 37A and the second oil passage 37B, and furthermore, in the event of a failure in the actuator circuit system, In order to reduce the resistance of the actuator body 34, a normally closed bypass valve 59 is interposed in another bypass path 60. Further, a rotation speed detector 61 such as a tacho generator is attached to the DC servo motor 32 to monitor the motor rotation speed and feed it back to the controller 31 to provide a rotation speed correction function. A piston position detector 62 is attached, and the detected value is fed back to the amplifier 30 for position correction.
なお１図中６３は給油バルブである。Note that 63 in Figure 1 is an oil supply valve.
このように構成された閉回路電気油圧アクチュエータパ
ッケージの作用は次のようになる、モータ３２により油
圧ポンプ３３を正回転させると、アクチュエータ本体３
４の第１油圧室３６Ａはポンプ吐出圧となり、この圧力
が第１分岐油路５３Ａを通じてアキュムレータ４０の第
１分割油室４５Ａに作用する。一方、第２油圧室３６Ｂ
はアキュムレータ４０の第２分割油室４５Ｂに通じてい
るものの、圧力バランスにより、第２油路３７Ｂの回路
圧は第１油路３７Ａの増圧分だけ減圧され。The action of the closed-circuit electro-hydraulic actuator package configured in this way is as follows. When the hydraulic pump 33 is rotated in the forward direction by the motor 32, the actuator body 3
4, the first hydraulic chamber 36A becomes the pump discharge pressure, and this pressure acts on the first divided oil chamber 45A of the accumulator 40 through the first branch oil path 53A. On the other hand, the second hydraulic chamber 36B
Although it communicates with the second divided oil chamber 45B of the accumulator 40, due to the pressure balance, the circuit pressure of the second oil passage 37B is reduced by the pressure increase in the first oil passage 37A.
初期圧力から低下するのである。この場合、第１、第２
分割油室４５Ａ、４５Ｂの受圧面積を等しくしているの
で、第１分割油室４５Ａの圧力増加量と第２分割油室４
５Ｂの圧力減少量は等しくなる。The pressure decreases from the initial pressure. In this case, the first and second
Since the pressure receiving areas of the divided oil chambers 45A and 45B are made equal, the amount of pressure increase in the first divided oil chamber 45A and the second divided oil chamber 4 are equal.
The amount of pressure reduction of 5B becomes equal.
したがって、第２分割油室４５Ｂに通じている第２油路
３７Ｂも等しく低下し、ポンプ３３の吸入側圧力は初期
圧力より低下するのである。この結果。Therefore, the second oil passage 37B communicating with the second divided oil chamber 45B is also lowered equally, and the suction side pressure of the pump 33 is lower than the initial pressure. As a result.
アクチュエータ本体３４のピストン３５前後の圧力差は
アキュムレータ４０の第１、第２分割油室４５Ａ、４５
Ｂの差圧と等しくなり、その差圧によって７クチユ工−
タ本体３４が駆動することになる。The pressure difference before and after the piston 35 of the actuator body 34 is caused by the first and second divided oil chambers 45A and 45 of the accumulator 40.
It becomes equal to the differential pressure of B, and due to that differential pressure
The main body 34 of the motor is driven.
このような作動特性を第３図に示す。アクチュこのよう
な作動特性を第３図に示す、アクチュエータ本体３４の
静止状態（中立位置）から（初期圧力Ｐｏ）ポンプ３３
を正方向に駆動すると、第１油圧室３６Ａの圧力は第３
図実線ｃ１のように増大し、他方の第２油圧室３６Ｂの
圧力は同図破線Ｃ２のように減少する。この差圧が有効
差圧となり、初期圧力とポンプ吐出圧の差圧の２倍の圧
力差を生じさせることができるのである。ポンプ３３の
逆回転時も同様である。Such operating characteristics are shown in FIG. The operating characteristics of the actuator are shown in FIG.
When the pressure in the first hydraulic chamber 36A is driven in the forward direction, the pressure in the first hydraulic chamber 36A increases
The pressure in the other second hydraulic chamber 36B increases as shown by the solid line c1 in the figure, and the pressure decreases as shown by the broken line C2 in the figure. This differential pressure becomes an effective differential pressure, and can generate a pressure difference twice as large as the differential pressure between the initial pressure and the pump discharge pressure. The same holds true when the pump 33 rotates in reverse.
斯かる実施例によれば、初期圧力を高く設定しても有効
差圧を大きくとることができ、従来と同様のポンプ能力
で２倍のアクチュエータ能力をもたせることができる。According to this embodiment, even if the initial pressure is set high, the effective differential pressure can be increased, and the actuator capacity can be doubled with the same pump capacity as the conventional pump.
また、初期圧力を高くシ。Also, increase the initial pressure.
アクチュエータ本体３４のピストン前後の油圧室３６Ａ
、３６Ｂ内圧力を制御できるので、アクチュエータ剛性
が向上し、特に安全性が要求される航空機塔載用として
有益な作用をなす。Hydraulic chamber 36A before and after the piston of actuator body 34
, 36B can be controlled, so the actuator rigidity is improved, which is particularly useful for use on aircraft towers where safety is required.
なお、上記実施例ではアキュムレータ４ｏの分割油室４
５Ａ、４５Ｂの受圧面積を等しくしたが、これはアクチ
ュエータ本体３４の仕様に基づいて定めればよく、例え
ばアクチュエータ本体を片ロッド構造としたり、中立点
からの往復移動に差異が生じるような場合には受圧面積
に差をもたせてもよい、したがって、航空機の舵面制御
用に供する他、操縦系統以外の油圧装置や一般の産業機
械やロボット等の駆動部にも充分適用でき、その効果に
は大なるものがある。In addition, in the above embodiment, the divided oil chamber 4 of the accumulator 4o
Although the pressure receiving areas of 5A and 45B are made equal, this can be determined based on the specifications of the actuator body 34. For example, if the actuator body has a single rod structure, or if there is a difference in reciprocating movement from the neutral point, may have different pressure receiving areas. Therefore, in addition to being used for controlling the control surfaces of aircraft, it can also be applied to hydraulic systems other than flight control systems and drive parts of general industrial machinery and robots, etc. There is something big.
以上説明したように、本発明によれば、モータ駆動のポ
ンプとアクチュエータ間で閉回路を形成し、アキュムレ
ータによって初期圧力を導入するようにしたものにおい
て、アキュムレータの油室を共通ピストンにより分割し
てポンプ前後の油路と各々接続するようにしたため、回
路内の圧力を常態においてアキュムレータ設定圧に等し
く保持しつつ、アクチュエータ片側が初期圧力より加圧
された場合にはアキュムレータ内の圧力バランスによっ
て他方は初期圧力から略同じ分だけ減圧され、有効差圧
を大きくでき、アクチュエータの両側で負荷に対向する
ことになり１通常のサーボバルブを用いた場合と同様の
アクチュエータ剛性を得ることができる。As explained above, according to the present invention, in a device in which a closed circuit is formed between a motor-driven pump and an actuator and initial pressure is introduced by an accumulator, the oil chamber of the accumulator is divided by a common piston. Since the oil passages are connected to the front and rear of the pump, the pressure in the circuit is maintained equal to the accumulator set pressure under normal conditions, but if one side of the actuator is pressurized above the initial pressure, the other side will change due to the pressure balance in the accumulator. The pressure is reduced by approximately the same amount from the initial pressure, increasing the effective differential pressure, and since both sides of the actuator face the load, it is possible to obtain the same actuator rigidity as when using a normal servo valve.
第１図は実施例の回路構成図、第２図はアキュムレータ
の断面図、第３図は実施例の圧力特性図第４図は従来例
の回路構成図、第５図は同圧力の特性図である。Fig. 1 is a circuit diagram of the embodiment, Fig. 2 is a sectional view of the accumulator, Fig. 3 is a pressure characteristic diagram of the embodiment, Fig. 4 is a circuit diagram of the conventional example, and Fig. 5 is a pressure characteristic diagram of the same. It is.
Claims (2)
とアクチュエータ本体の各油圧室とを接続して閉回路を
構成する油路を通じて回路圧が導入される油室と、ガス
が封入されたガス室とを備えたアキュムレータに対し、
前記油室を共通ピストンにより２分割し各分割室の各々
に前記アクチュエータ本体の各油圧室への回路圧を導入
させたことを特徴とする閉回路電気油圧アクチュエータ
パッケージ。(1) An oil chamber into which circuit pressure is introduced through an oil path that connects the suction and discharge ports of a reversible pump driven by an electric motor and each hydraulic chamber of the actuator body to form a closed circuit, and a gas filled gas chamber. For an accumulator with a chamber,
A closed circuit electro-hydraulic actuator package, characterized in that the oil chamber is divided into two by a common piston, and each divided chamber introduces circuit pressure to each hydraulic chamber of the actuator main body.
体の両油圧室面積比と同じ比率にしたことを特徴とする
特許請求の範囲第１項記載の閉回路電気油圧アクチュエ
ータパッケージ。(2) The closed circuit electrohydraulic actuator package according to claim 1, wherein the pressure receiving area of each of the divided chambers is set to the same ratio as the area ratio of both hydraulic chambers of the actuator main body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21767685A JPS6280302A (en) | 1985-09-30 | 1985-09-30 | Closed circuit electro-hydraulic actuator package |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP21767685A JPS6280302A (en) | 1985-09-30 | 1985-09-30 | Closed circuit electro-hydraulic actuator package |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6280302A true JPS6280302A (en) | 1987-04-13 |
| JPH0578685B2 JPH0578685B2 (en) | 1993-10-29 |
Family
ID=16707976
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP21767685A Granted JPS6280302A (en) | 1985-09-30 | 1985-09-30 | Closed circuit electro-hydraulic actuator package |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6280302A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02221702A (en) * | 1989-02-22 | 1990-09-04 | Nireco Corp | Electric hydraulic servomotor |
| WO2001088381A1 (en) * | 2000-05-19 | 2001-11-22 | Komatsu Ltd. | Hybrid machine with hydraulic drive device |
| JP2006200652A (en) * | 2005-01-21 | 2006-08-03 | Sanko Gosei Ltd | Actuator |
| DE102011005337A1 (en) * | 2011-03-10 | 2012-09-13 | Zf Friedrichshafen Ag | Drive arrangement for carrying out working movements in working machines |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58121302A (en) * | 1982-01-12 | 1983-07-19 | Hitachi Constr Mach Co Ltd | Controller for quantity of discharge of pump of hydraulic closed circuit |
-
1985
- 1985-09-30 JP JP21767685A patent/JPS6280302A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58121302A (en) * | 1982-01-12 | 1983-07-19 | Hitachi Constr Mach Co Ltd | Controller for quantity of discharge of pump of hydraulic closed circuit |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02221702A (en) * | 1989-02-22 | 1990-09-04 | Nireco Corp | Electric hydraulic servomotor |
| WO2001088381A1 (en) * | 2000-05-19 | 2001-11-22 | Komatsu Ltd. | Hybrid machine with hydraulic drive device |
| US6962050B2 (en) | 2000-05-19 | 2005-11-08 | Komatsu Ltd. | Hybrid machine with hydraulic drive device |
| JP2006200652A (en) * | 2005-01-21 | 2006-08-03 | Sanko Gosei Ltd | Actuator |
| DE102011005337A1 (en) * | 2011-03-10 | 2012-09-13 | Zf Friedrichshafen Ag | Drive arrangement for carrying out working movements in working machines |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0578685B2 (en) | 1993-10-29 |
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|---|---|---|---|
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