JPH01283489A - Direct operated type rotary servo valve - Google Patents
Direct operated type rotary servo valveInfo
- Publication number
- JPH01283489A JPH01283489A JP6099789A JP6099789A JPH01283489A JP H01283489 A JPH01283489 A JP H01283489A JP 6099789 A JP6099789 A JP 6099789A JP 6099789 A JP6099789 A JP 6099789A JP H01283489 A JPH01283489 A JP H01283489A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- rotary servo
- servo valve
- fluid
- valve body
- 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 claims abstract description 27
- BGPVFRJUHWVFKM-UHFFFAOYSA-N N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] Chemical compound N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] BGPVFRJUHWVFKM-UHFFFAOYSA-N 0.000 abstract description 5
- 238000001514 detection method Methods 0.000 abstract description 4
- 238000004804 winding Methods 0.000 description 12
- 238000013016 damping Methods 0.000 description 11
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000007935 neutral effect Effects 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Servomotors (AREA)
- Electrically Driven Valve-Operating Means (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は直動型ロータリサーボ弁に係り、特に可動部に
減衰を付与するに好適な弁の構成に関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a direct-acting rotary servo valve, and particularly to a valve configuration suitable for imparting damping to a movable part.
直動型ロータリサーボ弁としては、特開昭６１−１５３
０７４号に記載のようなロータリバルブを用い。As a direct-acting rotary servo valve, JP-A-61-153
Using a rotary valve as described in No. 074.
弁体の角変位を検出、フィードバックして弁体の位置決
めを行うとともに、弁体の角速度を検出、フィードバッ
クして可動部に減衰を付与する方法が採られていた。A method has been adopted in which the angular displacement of the valve body is detected and fed back to determine the position of the valve body, and the angular velocity of the valve body is detected and fed back to provide damping to the movable part.
しかし、この方法では角速度検出器を用いろために弁の
摺造が複雑となり大きさが増すだけでなく、角速度信号
帰環のための制御回路を必要とするために制御装置が複
雑、高価となるなどの問題があった。However, since this method uses an angular velocity detector, the valve not only has a complicated sliding structure and an increased size, but also requires a control circuit for returning the angular velocity signal, making the control device complicated and expensive. There were problems such as:
本発明の目的は１以上のような従来技術の問題点を解消
するため、角速度検出を要せずして可動部に減衰を付与
し得る直動型ロータリサーボ弁を提供することにある。SUMMARY OF THE INVENTION An object of the present invention is to provide a direct-acting rotary servo valve that can provide damping to a movable part without requiring angular velocity detection, in order to solve one or more problems of the prior art.
上記目的は、弁体に一体的に結合された回転子と磁気回
路を構成する磁石及びヨークとの間に粘性流体を満たす
ことによって達成される。The above object is achieved by filling a viscous fluid between the rotor, which is integrally coupled to the valve body, and the magnet and yoke that constitute the magnetic circuit.
本発明によれば１回転子が回動すると１回転子近傍の流
体中に速度勾配が生ずるため流体の粘性によって流体中
に剪断応力が生じ、この剪断応力によって回転子には回
動に対する抵抗力が作用する。この際、剪断応力は速度
勾配に比例するため回転子およびこれと結合された弁体
には角速度に比例した制動力が作用する。このようにし
て流体の粘性により可動部に制動、すなわち減衰を与え
ることができる。According to the present invention, when one rotor rotates, a velocity gradient is generated in the fluid near the first rotor, so a shear stress is generated in the fluid due to the viscosity of the fluid, and this shear stress causes the rotor to resist the rotation. acts. At this time, since the shear stress is proportional to the velocity gradient, a braking force proportional to the angular velocity acts on the rotor and the valve body connected thereto. In this way, the viscosity of the fluid can provide damping, or damping, to the movable part.
以下１本発明の一実施例を第１図ないし第３図により説
明する。An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.
第１図は本考発明よる直動型ロータリサーボ弁の一実施
例を示す縦断面図、第２図は第１図の八−Ａ線断面図、
第３図は第１図のＢ−Ｂ線断面図である。FIG. 1 is a longitudinal cross-sectional view showing an embodiment of a direct-acting rotary servo valve according to the present invention, FIG. 2 is a cross-sectional view taken along line 8-A in FIG.
FIG. 3 is a sectional view taken along the line B--B in FIG. 1.
ケーシング１内には弁体２が回動可能に設けられており
、弁体２の一部には円板状の回転子３が一体的に結合さ
れている。一方、磁石４およびヨーク５により磁気回路
が構成されており１回転子３は磁石４およびヨーク５に
対し所定の間隙をもってこれらにはさまれるように配設
されている。A valve body 2 is rotatably provided within the casing 1, and a disc-shaped rotor 3 is integrally connected to a portion of the valve body 2. On the other hand, a magnetic circuit is constituted by the magnet 4 and the yoke 5, and the first rotor 3 is arranged so as to be sandwiched between the magnet 4 and the yoke 5 with a predetermined gap therebetween.
また、弁体２には制御室６および７が設けられており、
ケーシング１には供給ボート８．排出ボート９、制御ボ
ート１０および１１が設けられている。さらに弁体２の
一端には角変位検出器１２が連絡されており、他端には
ねじりバネ１３が一体的に結合され、ねじりバネ１３の
端部は雄ネジに成形されていてナツト１４により中立位
置を調整し固定できるように構成されている。そして、
回転子３と、磁石４およびヨーク５で構成された磁気回
路との間の空間１５には粘性流体が満たされており、こ
の流体と、弁により制御される作動流体とを分離するた
めにシール部材１６が設けられている。また、第２図に
示すように、回転７−３には巻線３ａが角ピッチＴで円
周方向に複数施されており、巻線３ａの巻き方向は相隣
３巻線の巻き方向が互いに反対の向きとなるように構成
されている。さらに、磁石４は巻線３ａと同じ角ピッチ
ψで円周方向に交互に極性が反対となるように構成され
ている。Further, the valve body 2 is provided with control chambers 6 and 7,
The casing 1 has a supply boat 8. A discharge boat 9 and control boats 10 and 11 are provided. Furthermore, an angular displacement detector 12 is connected to one end of the valve body 2, and a torsion spring 13 is integrally connected to the other end. It is configured so that the neutral position can be adjusted and fixed. and,
A space 15 between the rotor 3 and a magnetic circuit made up of magnets 4 and yoke 5 is filled with viscous fluid, and a seal is provided to separate this fluid from the working fluid controlled by the valve. A member 16 is provided. Further, as shown in Fig. 2, a plurality of windings 3a are arranged in the circumferential direction on the rotation 7-3 at an angular pitch T, and the winding direction of the winding 3a is the same as that of the three adjacent windings. They are configured to face in opposite directions. Further, the magnets 4 are configured to have the same angular pitch ψ as the winding 3a and have opposite polarities alternately in the circumferential direction.
次に、本実施例の作用について説明する。Next, the operation of this embodiment will be explained.
第２図に示すように、中立状態において、回転子３は巻
線３ａの境界が磁石４の分割位置に対して角度θ＝−だ
けずれた位置に設定されている。As shown in FIG. 2, in the neutral state, the boundaries of the windings 3a of the rotor 3 are set at positions offset from the division positions of the magnets 4 by an angle θ=-.
いま磁界中に置かれた巻線３ａに電流を流すと電磁力が
発生する。このとき、巻線３ａは交互に巻き方向が反対
となるように構成されているから電流は矢印１７の向き
に流れる。一方、磁石４は図中に示すように円周方向に
交互に極性が反対となるように構成されているから磁界
の向きが交互に反対の向きとなっている。したがって巻
線３ａに作用する電磁力は全て同じ向きとなり、その結
果回転子３に矢印１８の向きの回動力が発生する。When current is passed through the winding 3a placed in the magnetic field, an electromagnetic force is generated. At this time, since the windings 3a are configured so that the winding directions are alternately opposite, the current flows in the direction of the arrow 17. On the other hand, as shown in the figure, the magnets 4 are constructed so that the polarities are alternately opposite in the circumferential direction, so that the directions of the magnetic fields are alternately opposite. Therefore, all the electromagnetic forces acting on the winding 3a are in the same direction, and as a result, a rotating force in the direction of the arrow 18 is generated in the rotor 3.
この回動力によって弁体２も矢印１８の向きに回動する
。このとき、第３図に示すように、弁体２の制御室６は
アクチュエータに連通ずる供給ボート８と１、また制御
室７は排出ボート９とそれぞれつながるから、図中の矢
印で示すように、作動流体は制御ボート１０に供給され
、制御ボート１１から排出される。一方、巻線３ａに流
す電流の向きを反対にすれば１回動力は反対の向きとな
り、弁体は矢印１８と反対の向きに回動するから、作動
流体は制御ボート１１に供給され、制御ボート１０から
排出されるようになる。したがって、巻線３ａに流す電
流の向きと大きさを制御することにより回転子３および
弁体２を±θまでの角度範囲で回動させることができ、
さらに角変位検出器１２により弁体２の角変位を検出し
フィードバックすれば弁体を正確に位置決めし作ｌ１ｌ
ｓ流体の流れの向きと流最を制御することができる。し
かし。This rotational force also causes the valve body 2 to rotate in the direction of the arrow 18. At this time, as shown in FIG. 3, the control chamber 6 of the valve body 2 is connected to the supply boats 8 and 1 which communicate with the actuator, and the control chamber 7 is connected to the discharge boat 9, so as shown by the arrows in the figure. , the working fluid is supplied to the control boat 10 and discharged from the control boat 11. On the other hand, if the direction of the current flowing through the winding 3a is reversed, the power will be in the opposite direction, and the valve body will rotate in the opposite direction to the arrow 18, so the working fluid will be supplied to the control boat 11, and the control boat 11 will be supplied with the working fluid. The water will be discharged from the boat 10. Therefore, by controlling the direction and magnitude of the current flowing through the winding 3a, the rotor 3 and the valve body 2 can be rotated within an angular range of ±θ.
Furthermore, if the angular displacement of the valve body 2 is detected by the angular displacement detector 12 and fed back, the valve body can be accurately positioned and operated.
s The direction and flow direction of the fluid can be controlled. but.
より高速で制御するためには回転子３など可動部の動き
に適度な減衰を付与しないと発振現象などを生じてしま
う、しかしながら、本実施例においては、回転子３と、
磁石４およびヨーク５で構成された磁気回路との間の空
間１５に粘性流体が満たされているから、回転子３が回
動する際、回転子３の近傍の流体中に速度勾配が生ずる
ため流体の粘性により流体中には速度勾配に比例した剪
断応力が生じ、この剪断応力によって回転子３および弁
体２の動きに対して角速度に比例した制御力すなわち減
衰力が作用する。これにより作動流体の流れをより高速
で正確に制御することができる。In order to control at a higher speed, oscillation phenomena will occur unless appropriate damping is applied to the movement of the rotor 3 and other movable parts.However, in this embodiment, the rotor 3 and the
Since the space 15 between the magnet 4 and the magnetic circuit composed of the yoke 5 is filled with viscous fluid, when the rotor 3 rotates, a velocity gradient is generated in the fluid near the rotor 3. Due to the viscosity of the fluid, a shear stress proportional to the velocity gradient is generated in the fluid, and this shear stress exerts a control force, that is, a damping force, proportional to the angular velocity on the movement of the rotor 3 and the valve body 2. This allows for faster and more accurate control of the flow of the working fluid.
したがって、本実施例によれば、角速度検出を要せずし
て可動部に減衰を付与することができ。Therefore, according to this embodiment, damping can be applied to the movable portion without requiring angular velocity detection.
弁の構造が簡単となり小形で商値となるだけでなく、角
速度信号帰環のための制御回路が不要となるため制御装
置も簡単で安価となる。Not only is the structure of the valve simplified, resulting in a small size and commercial value, but also the control device is simple and inexpensive because a control circuit for returning the angular velocity signal is not required.
なお、減衰を得るための粘性流体を作動流体と同じとし
ても良く、この場合、第１図に示したシール部材１６は
不要となる。Note that the viscous fluid for obtaining damping may be the same as the working fluid, and in this case, the sealing member 16 shown in FIG. 1 becomes unnecessary.
また、第４図に示すように、減衰を得るための流体を磁
性粘性流体１９としても良い。Further, as shown in FIG. 4, the fluid for obtaining damping may be a magnetorheological fluid 19.
以上説明したように１本発明によれば、角速度検出を要
せずして可動部に減衰を付与することができるため、弁
の構造が簡単となり小形で安価となるだけでなく、角速
度信号帰還のための制御回路が不要となるため制御装置
も簡単で安価となるなど、技術上だけでなく経済上の効
果も得られる。As explained above, according to the present invention, it is possible to apply damping to the movable part without requiring angular velocity detection, which not only simplifies the structure of the valve, makes it compact and inexpensive, but also enables angular velocity signal feedback. Since there is no need for a control circuit for this, the control device is simple and inexpensive, which provides not only technical but also economic benefits.
第１図は本発明の一実施例の直動型ロータリサーボ弁を
示す縦断面図、第２図は第１図のＡ−Ａ線断面図、第３
図は第１図のＢ−Ｂ線断面図、第４図は本発明の他の実
施例の直動型ロータリサーボ弁を示す縦断面図である。
１・・・ケーシング、２・・・弁体、３・・・回転子、
４・・・磁石、５・・・ヨーク、１５・・・流体を満た
す空間、１９・・・磁性粘性流体。
代理人 弁理士 小川勝馬パ・□−゛−゛・。
一FIG. 1 is a vertical sectional view showing a direct-acting rotary servo valve according to an embodiment of the present invention, FIG. 2 is a sectional view taken along line A-A in FIG. 1, and FIG.
The figure is a sectional view taken along the line B--B in FIG. 1, and FIG. 4 is a longitudinal sectional view showing a direct acting rotary servo valve according to another embodiment of the present invention. 1...Casing, 2...Valve body, 3...Rotor,
4... Magnet, 5... Yoke, 15... Space filled with fluid, 19... Magneto-rheological fluid. Agent Patent Attorney Katsuma Ogawa Pa・□−゛−゛・. one
Claims (1)
れた弁体と、該弁体に一体的に結合された回転子と、該
回転子を回動させるための磁気回路を構成する磁石及び
ヨークとを備えた直動型ロータリサーボ弁において、前
記回転子と前記磁石及び前記ヨークとの間に粘性流体を
有することを特徴とする直動型ロータリサーボ弁。1. A casing, a valve body rotatably provided within the casing, a rotor integrally coupled to the valve body, and a magnet constituting a magnetic circuit for rotating the rotor. A direct-acting rotary servo valve comprising a yoke, the direct-acting rotary servo valve having a viscous fluid between the rotor, the magnet, and the yoke.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6099789A JPH01283489A (en) | 1989-03-15 | 1989-03-15 | Direct operated type rotary servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6099789A JPH01283489A (en) | 1989-03-15 | 1989-03-15 | Direct operated type rotary servo valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01283489A true JPH01283489A (en) | 1989-11-15 |
| JPH0341711B2 JPH0341711B2 (en) | 1991-06-24 |
Family
ID=13158580
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6099789A Granted JPH01283489A (en) | 1989-03-15 | 1989-03-15 | Direct operated type rotary servo valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01283489A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011112212A (en) * | 2009-11-30 | 2011-06-09 | Takara Belmont Co Ltd | Electric valve |
| KR20160128914A (en) * | 2015-04-29 | 2016-11-08 | 독터. 인제니어. 하.체. 에프. 포르쉐 악티엔게젤샤프트 | Rotary fluid regulator |
| JP2016211737A (en) * | 2015-04-29 | 2016-12-15 | ドクター エンジニール ハー ツェー エフ ポルシェ アクチエンゲゼルシャフトＤｒ． Ｉｎｇ． ｈ．ｃ． Ｆ． Ｐｏｒｓｃｈｅ Ａｋｔｉｅｎｇｅｓｅｌｌｓｃｈａｆｔ | Rotary fluid adjusting device |
-
1989
- 1989-03-15 JP JP6099789A patent/JPH01283489A/en active Granted
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011112212A (en) * | 2009-11-30 | 2011-06-09 | Takara Belmont Co Ltd | Electric valve |
| KR20160128914A (en) * | 2015-04-29 | 2016-11-08 | 독터. 인제니어. 하.체. 에프. 포르쉐 악티엔게젤샤프트 | Rotary fluid regulator |
| JP2016211737A (en) * | 2015-04-29 | 2016-12-15 | ドクター エンジニール ハー ツェー エフ ポルシェ アクチエンゲゼルシャフトＤｒ． Ｉｎｇ． ｈ．ｃ． Ｆ． Ｐｏｒｓｃｈｅ Ａｋｔｉｅｎｇｅｓｅｌｌｓｃｈａｆｔ | Rotary fluid adjusting device |
| JP2016211738A (en) * | 2015-04-29 | 2016-12-15 | ドクター エンジニール ハー ツェー エフ ポルシェ アクチエンゲゼルシャフトＤｒ． Ｉｎｇ． ｈ．ｃ． Ｆ． Ｐｏｒｓｃｈｅ Ａｋｔｉｅｎｇｅｓｅｌｌｓｃｈａｆｔ | Rotary fluid adjustment device |
| US9939079B2 (en) | 2015-04-29 | 2018-04-10 | Dr. Ing. H.C.F. Porsche Aktiengesellschaft | Rotary fluid regulator |
| US10385984B2 (en) | 2015-04-29 | 2019-08-20 | Dr. Ing H.C.F. Porsche Aktiengesellschaft | Rotary fluid regulator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0341711B2 (en) | 1991-06-24 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |