JPS63152779A - Rotary valve for pressurized fluid path - Google Patents
Rotary valve for pressurized fluid pathInfo
- Publication number
- JPS63152779A JPS63152779A JP30254686A JP30254686A JPS63152779A JP S63152779 A JPS63152779 A JP S63152779A JP 30254686 A JP30254686 A JP 30254686A JP 30254686 A JP30254686 A JP 30254686A JP S63152779 A JPS63152779 A JP S63152779A
- Authority
- JP
- Japan
- Prior art keywords
- swing
- supply
- port
- valve body
- cylindrical valve
- 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
- 239000012530 fluid Substances 0.000 title claims abstract description 24
- 238000004891 communication Methods 0.000 claims abstract description 4
- 230000008878 coupling Effects 0.000 abstract 1
- 238000010168 coupling process Methods 0.000 abstract 1
- 238000005859 coupling reaction Methods 0.000 abstract 1
- 230000007246 mechanism Effects 0.000 description 12
- 239000000853 adhesive Substances 0.000 description 10
- 230000001070 adhesive effect Effects 0.000 description 10
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 238000005516 engineering process Methods 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 239000011248 coating agent Substances 0.000 description 2
- 238000000576 coating method Methods 0.000 description 2
- 239000004744 fabric Substances 0.000 description 1
- 238000007667 floating Methods 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Landscapes
- Multiple-Way Valves (AREA)
Abstract
Description
【発明の詳細な説明】
O産業上の利用分野
本発明は、加圧流体路における加圧流体の供給を断接す
る。ための弁機構に関するものである。例えば、流体塗
着装置において加圧流体源とノズルとの間に介装する流
体分配機構に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention disconnects and disconnects the supply of pressurized fluid in a pressurized fluid path. This relates to a valve mechanism for For example, it relates to a fluid distribution mechanism interposed between a source of pressurized fluid and a nozzle in a fluid applicator.
O従来の技術およびその問題点
加圧流体路の弁機構(流体分配機構)として、特公昭5
5−44672号「流体塗着装置」が公知である。該装
置における流体分配機構においてはバルブ部材は軸方向
に摺動している。O Conventional technology and its problems As a valve mechanism (fluid distribution mechanism) for a pressurized fluid path,
No. 5-44672 ``Fluid applicator'' is known. In the fluid distribution mechanism of the device, the valve member slides axially.
また、油圧回路の弁機構においても、弁ハウジング内の
弁体を軸方向に摺動させている。Furthermore, in the valve mechanism of the hydraulic circuit, the valve body inside the valve housing is slid in the axial direction.
上記の公知技術においては、軸方向の摺動により供給ポ
ートとを連断するものであるから、迅速かつ頻繁に断接
を繰り返すには不適当である。In the above-mentioned known technology, since the connection with the supply port is made by sliding in the axial direction, it is not suitable for rapidly and frequently repeating connection and disconnection.
0本発明の目的および目的達成のための手段本発明の目
的は、公知技術の上記問題点を解決すべく、加圧流体の
供給の断接を迅速かつ頻繁に操作可能とするとともに、
供給量を所望の設定量に制御自在とすることである。0 OBJECTS OF THE INVENTION AND MEANS FOR ACHIEVING THE OBJECTS An object of the present invention is to solve the above-mentioned problems of the known technology by making it possible to quickly and frequently disconnect and disconnect the supply of pressurized fluid.
It is possible to freely control the supply amount to a desired set amount.
本発明は、円筒体の周面に弁溝(21)を形成してなる
円筒弁体(2)と、前記円筒弁体(2)を密封状態で回
転自在に支持するとともに円筒弁体(2)の弁溝(21
)と連通可能な位置に開口した供給ポート(Ill、吐
出ポート(12)および戻りポート(+3)を有する弁
ハウジング(+1 とを設け、円筒弁体(2)を揺動さ
せて、供給ポート(If)と吐出ポート(I2)との連
通、供給ポート(+ 1)と吐出ポート(12)との遮
断を交互に行うとともに、円筒弁体(2)と揺動手段(
3)の駆動軸(30)とを揺動中心設定手段(4)を介
して連結して一回の揺動に際しての加圧流体の供給時間
を変更自在とする。The present invention provides a cylindrical valve body (2) having a valve groove (21) formed on the circumferential surface of the cylindrical body, and a cylindrical valve body (2) that rotatably supports the cylindrical valve body (2) in a sealed state. ) valve groove (21
) is provided with a valve housing (+1) having a supply port (Ill), a discharge port (12), and a return port (+3) that are open at a position where it can communicate with the supply port ( If) and the discharge port (I2), and the supply port (+1) and the discharge port (12) are alternately disconnected, and the cylindrical valve body (2) and the swinging means (
3) is connected to the drive shaft (30) via the swing center setting means (4), so that the supply time of pressurized fluid during one swing can be freely changed.
O実施例
図面に示す実施例は、接着剤塗布機構の弁機構として本
発明を実施した場合を示し、ロータリーバルブ(Alを
、内部に円筒形状の弁室(a)を形成した弁ハウジング
(11と、前記弁室(11)内に嵌合した円筒形状の円
筒弁体(2)とで構成する。O Example The example shown in the drawings shows a case where the present invention is implemented as a valve mechanism of an adhesive application mechanism. and a cylindrical valve body (2) having a cylindrical shape fitted into the valve chamber (11).
弁ハウジング(11の吐出ポート(12)は、ノズル部
材(Bl内の流路(bl と連通し、供給ポート(11
)および戻りポート(13)はパイプ接続部材(C)内
の流路(CI> (C2)にそれぞれ連通し、パイプ(
図示省略)を介して加圧ポンプ(図示省略)、接着剤タ
ンク(図示省略)にそれぞれ連通している。The discharge port (12) of the valve housing (11) communicates with the flow path (bl) in the nozzle member (Bl) and communicates with the supply port (11).
) and the return port (13) respectively communicate with the flow path (CI> (C2)) in the pipe connecting member (C), and the pipe (
It communicates with a pressure pump (not shown) and an adhesive tank (not shown) via a pressure pump (not shown).
上述の供給ポート(11)、吐出ポート(12)および
戻りポート(13)は、第2図に示すごとく、吐出ポー
ト(12)を通る綜X−Xに対し供給ポート(11)と
戻りポート(13)とを互いに逆方向に偏位させて配置
し、円筒弁体(2)の周面に、供給ポート(11)と吐
出ポート(12)とを連通状態とするに十分な長さを有
する部分リング形状の弁溝(21)を設け、円筒弁体(
2)の揺動に伴って、第3図に示すごとく、供給ポート
(11)と吐出ポート(12)とを連通〈供給〉(0図
)、供給ポート(11)と戻りポート(13)とを連通
に供給遮断> (b図)とに変更して弁作用する。な
お、必要に応じ、すべてのポート(11) (121(
13)を互いに遮断、吐出ポート(12)と戻りポート
(13)とを連通の状態が付加されるようにポート(1
1)(12) (13)の相互位置関係および弁溝(2
1)の長さを設定することもできる。上述の円筒弁体(
2)は弁室(Al内にあってその周面ば弁ハウジング(
1)の内周面と摺動して円筒弁体(2)を回転自在とす
るとともに、円筒弁体(2)の−面より一体的に突出し
た軸部(22)および他面より一体的に突出した軸部(
23)を、軸受(241(25) 、ゴムリング(26
) (27)およびリングシム(28) (29)を介
して、弁ハウジング(2)に回転自在に支持させる。The above-mentioned supply port (11), discharge port (12), and return port (13) are connected to the supply port (11) and return port ( 13) are arranged offset in opposite directions to each other, and have a length sufficient to communicate the supply port (11) and the discharge port (12) on the circumferential surface of the cylindrical valve body (2). A partial ring-shaped valve groove (21) is provided, and a cylindrical valve body (
2), as shown in Fig. 3, the supply port (11) and the discharge port (12) are connected (supply) (Fig. 0), and the supply port (11) and the return port (13) are connected. The valve operates by changing the supply to the communication line and shutting off the supply (Figure b). In addition, all ports (11) (121(
13) are mutually isolated, and the discharge port (12) and return port (13) are placed in communication with each other.
1) (12) (13) mutual positional relationship and valve groove (2)
1) You can also set the length. The above-mentioned cylindrical valve body (
2) The valve chamber (located in Al, and its circumferential surface facing the valve housing (
The cylindrical valve body (2) is made rotatable by sliding on the inner circumferential surface of the cylindrical valve body (2), and the shaft part (22) integrally protrudes from the negative face of the cylindrical valve body (2), and the shaft part (22) integrally protrudes from the other face of the cylindrical valve body (2). The protruding shaft part (
23), bearing (241 (25), rubber ring (26)
) (27) and ring shims (28) and (29), the valve housing (2) is rotatably supported.
軸(22)と一体の延長軸(31)を筒体(32)を介
して駆動軸(30)と連動し、該駆動軸(30)を接手
(35)を介して揺動手段(3)で駆動して円筒弁体(
2)を間欠回動(揺動)させるべく構成する。An extension shaft (31) integrated with the shaft (22) is interlocked with a drive shaft (30) through a cylinder (32), and the drive shaft (30) is connected to the swinging means (3) through a joint (35). to drive the cylindrical valve body (
2) is configured to rotate (swing) intermittently.
つぎに、揺動中心角設定手段(4)を説明する。Next, the swing center angle setting means (4) will be explained.
揺動中心角設定手段(4)は、揺動手段(3)の駆動軸
(30)の駆動中心位置(又は揺動駆動始点位置)と、
ロータリーバルブの円筒弁体(2)の揺動中心位置(又
は揺動始点位置)との相対位置関係を設定するものであ
り、第1図に示す実施例においては、延長軸(31)と
係合部(31a)を介して一体的に回転するキャップ(
32)と、駆動軸(30)とスプライン係合して一体的
に回転する筒体(33)とを、遊合させて、キャップ(
32)と筒体(33)とを相対的に回動自在とするとと
もに、ビン(34)により所望の相対角度位置で延長軸
(31)と駆動軸(30)とを連結自在とする。The swing center angle setting means (4) determines the drive center position (or swing drive starting point position) of the drive shaft (30) of the swing means (3);
This is to set the relative positional relationship with the swing center position (or swing start point position) of the cylindrical valve body (2) of the rotary valve, and in the embodiment shown in FIG. The cap (
A cap (
32) and the cylindrical body (33) are relatively rotatable, and the extension shaft (31) and the drive shaft (30) can be freely connected at a desired relative angular position by means of a pin (34).
上述の相対角度位置の変更は手動で行なうものであるが
、第8図に示す実施例においては動力式とし、上述の構
成の揺動中心角設定手段(4)は駆動軸(3)と円筒弁
体(2)との相対零位置の調整用とする。Although the above-mentioned change in the relative angular position is performed manually, in the embodiment shown in FIG. Used for adjusting the relative zero position with the valve body (2).
第8図を参照して、動力式揺動中心角設定手段(4°)
は、ロータリーバルブ(A)の円筒弁体(2)と伝動す
る駆動軸(30)と、後述の揺動手段(3)と伝動する
中間軸(40)とを駆動ヘリカルギヤ(41)と従動ヘ
リカルギヤ(42)とを介して伝動し、従動ヘリカル奪
ヤ(42)を駆動軸(30)とスプライン係合させて軸
方向に移動自在とし、従動ヘリカルギヤ(42)の軸方
向移動により中間軸(40)と独立して駆動軸(30)
を回動させるべく構成するとともに、駆動ヘリカルギヤ
(42)の支持体(43)と一体の摺動体(44)をね
じ軸(45)と螺合させてねじ軸(45)の回転により
従動ヘリカルギヤ(42)を軸方向に移動させるべく構
成し、ねじ軸(45)と伝動するサーボモータ等の制御
自在な駆動手段(46)を設け、駆動手段(46)の制
御、例えばサーボモータに対する電気的制御により駆動
軸(30)を中間軸(40)に対し所定角度だけ相対的
に回動自在として構成する。Referring to Fig. 8, power type swing center angle setting means (4°)
is a drive shaft (30) that transmits power to the cylindrical valve body (2) of the rotary valve (A), an intermediate shaft (40) that transmits power to the swinging means (3) described below, and a drive helical gear (41) and a driven helical gear. (42), and the driven helical gear (42) is spline-engaged with the drive shaft (30) to be freely movable in the axial direction, and by the axial movement of the driven helical gear (42), the intermediate shaft (40) ) and independently the drive shaft (30)
The sliding body (44) integrated with the support (43) of the drive helical gear (42) is screwed onto the screw shaft (45), and the driven helical gear (45) is rotated by the rotation of the screw shaft (45). 42) is configured to move in the axial direction, and is provided with a controllable drive means (46) such as a servo motor that is transmitted to the screw shaft (45), and the drive means (46) is controlled, for example, by electrical control of the servo motor. The drive shaft (30) is configured to be rotatable relative to the intermediate shaft (40) by a predetermined angle.
揺動手段(3)としては、オシレーテイングドライブ、
バレルカム等の各種のカム機構、その他の電動駆動機構
を用いることができる。The rocking means (3) includes an oscillating drive,
Various cam mechanisms such as barrel cams and other electric drive mechanisms can be used.
また、カム機構の入力軸に直接または間接的に、サーボ
モータその他の速度制御用モータ(5)を連結すること
により、ロータリーバルブの回転運動を制御し、任意の
加圧流体の吐出時間が設定可能である。In addition, by directly or indirectly connecting a servo motor or other speed control motor (5) to the input shaft of the cam mechanism, the rotational movement of the rotary valve can be controlled and the discharge time of any pressurized fluid can be set. It is possible.
延長軸(31)と伝動するギヤまたはプーリを、サーボ
モータ、パルスモータ等の電気的揺動駆動手段(3″)
の出力軸に直結して、サーボモータ等の電気的制御によ
り円筒弁体(2)を所望の揺動角で揺動運動させるべく
構成することもできる。The extension shaft (31) and the transmission gear or pulley are connected to an electric swing drive means (3″) such as a servo motor or a pulse motor.
The cylindrical valve body (2) can also be directly connected to the output shaft of the valve body and configured to swing at a desired swing angle by electrical control of a servo motor or the like.
なお、延長軸(11)と反対側へ突出させた第2延長軸
(31“)を設け、′適宜の伝動手段を介して他のロー
タワーバルブの延長軸と接続して、単一の駆動軸(30
)より動力を経て複数個のロータリーバルブを駆動すべ
く構成することもできる。In addition, a second extension shaft (31") is provided that protrudes to the opposite side of the extension shaft (11), and is connected to the extension shaft of another rotor tower valve via an appropriate transmission means to provide a single drive. Axis (30
) can also be configured to drive a plurality of rotary valves via power.
つぎに、本発明のロータリーバルブの弁作用を説明する
。Next, the valve action of the rotary valve of the present invention will be explained.
円筒弁体(2)は、揺動手段(3)により駆動されて所
定角度(例えば90@)で連続的に揺動する。The cylindrical valve body (2) is driven by the swinging means (3) and swings continuously at a predetermined angle (for example, 90@).
円筒弁体(2)の揺動に伴って、第3図(a) 2(b
)間のα角度については、供給ポート(Illと吐出ポ
ート(12)とを遮断するとともに供給ポート(11)
と戻りポート(13)とを連通させる〔加圧流体く接着
剤)のノズル(B)への供給を停止するとともに戻りポ
ート(13)はタンクを経て加圧流体を循環させる〕。As the cylindrical valve body (2) swings, Fig. 3(a) 2(b)
), the supply port (Ill) and the discharge port (12) are blocked, and the supply port (11)
and a return port (13) [the supply of pressurized fluid and adhesive to the nozzle (B) is stopped, and the return port (13) circulates the pressurized fluid through the tank].
第3図(a) g(c1間のβ角度については、供給ポ
ート(11)と吐出ポート(I2)とを連通ずる(ノズ
ル(B)へ加圧流体く接着剤)を供給する〕。FIG. 3(a) g (For the β angle between c1, the supply port (11) and the discharge port (I2) are communicated (pressurized fluid or adhesive is supplied to the nozzle (B))].
即ち、ロータリーバルブのON・OFF連続切替作用(
弁作用)により、1ストロークのうち、(a)→(e3
→(A)の2β°の区間だけ加圧流体(接着剤)がノズ
ルに間欠的に供給され、(a)→(bl→(a)の2α
0の区間では供給が停止される。In other words, the ON/OFF continuous switching action of the rotary valve (
Due to valve action), (a) → (e3
→ Pressurized fluid (adhesive) is intermittently supplied to the nozzle only in the 2β° section of (A), and (a) → (bl → 2α of (a)
Supply is stopped in the 0 section.
なお、第4図、第5図における供給区間β、遮断区間α
の角度の選定(即ち、加圧流体の供給区間、供給タイミ
ングの決定)は、揺動手段(3)の揺動角の変更〔公知
のカム手段(オシレーテイングドライブ)において、5
″〜+20’の揺動角を選択自在とするものが存在する
〕により第5図に示すごとく簡単に変更することができ
る。In addition, the supply section β and the cutoff section α in FIGS. 4 and 5
The selection of the angle (that is, the determination of the supply section and supply timing of the pressurized fluid) is performed by changing the swing angle of the swing means (3) [In the known cam means (oscillating drive),
There is a device that allows the swing angle to be freely selected from 20' to +20', so it can be easily changed as shown in FIG.
更に、揺動手段(3)に接続したサーボモータ等の速度
制御により、円筒弁(1)の揺動速度を変更することに
よっても、第6図に示すごくと供給状態は変化する。Furthermore, the supply state shown in FIG. 6 can also be changed by changing the swing speed of the cylindrical valve (1) by controlling the speed of a servo motor or the like connected to the swing means (3).
つぎに、揺動中心設定手段(4)の作用による供給量制
御について説明する。Next, the supply amount control by the action of the swing center setting means (4) will be explained.
揺動手段(3)による揺動角が一定(例えば90”とし
ても、第3図(al に対応する位置(駆動軸とロータ
リーバルブとの間の仮想0点)を中心として、子方向ま
たは一方向に相対角度位置偏位させることによって吐出
(供給)区間βと遮断区間αとの割合を変化させること
ができ、第7図に示すごとく供給量を変化させることが
できる。Even if the swinging angle by the swinging means (3) is constant (for example, 90"), the swinging angle may be fixed (for example, 90"), but the swinging angle may be fixed (for example, 90") in the child direction or one direction, centered on the position (virtual 0 point between the drive shaft and the rotary valve) corresponding to FIG. 3 (al). By shifting the relative angular position in the direction, the ratio between the discharge (supply) section β and the cutoff section α can be changed, and the supply amount can be changed as shown in FIG.
設定中心設定手段(4)および機械的揺動手段(カム手
段)により機械的に供給量を制御可能とするもので加圧
流体の供給量の調節にあたり電気的知識を不用として保
守作業を容易とするものであるが、電気的揺動手段を設
けた場合は、電気的制御により、例えば、サーボモータ
の速度制御等により円筒弁体の揺動角を変更して加圧流
体の供給タイミング、供給量の変更(接着剤の塗布長さ
の変更)ができ、自動接着制御装置に本発明のロータリ
ーバルブを組込むと、被接着物の搬送速度。The supply amount can be controlled mechanically using the setting center setting means (4) and the mechanical swinging means (cam means), and maintenance work is facilitated by eliminating the need for electrical knowledge when adjusting the supply amount of pressurized fluid. However, when an electric swinging means is provided, the swinging angle of the cylindrical valve body is changed by electrical control, for example, by speed control of a servo motor, etc., to control the supply timing and supply of pressurized fluid. By incorporating the rotary valve of the present invention into an automatic adhesive control device, it is possible to change the amount of adhesive (change the length of adhesive application), and the conveyance speed of the adhered object.
接着長さ・巾の変化による所用塗布量の変化に、自動め
に対応することができる。It can automatically respond to changes in the required coating amount due to changes in adhesive length and width.
上述の円筒弁体(2)の回転による弁作用に際し、)ゴ
ムリング(26) (27)により上方および下方より
弾性押圧して浮動状態とし、かつシール効果により加圧
流体の漏出を防止するとともに、円筒弁体(2)の上面
および下面の加工精度を低くすることができる。When the above-mentioned cylindrical valve body (2) rotates to act as a valve, it is elastically pressed from above and below by the rubber rings (26) and (27) to create a floating state, and the sealing effect prevents leakage of pressurized fluid. , the machining accuracy of the upper and lower surfaces of the cylindrical valve body (2) can be lowered.
O発明の効果
本発明は、弁ハウジングと円筒弁体とで構成したので、
ロータリバルブ構造により加圧流体に対する迅速かつ頻
繁な弁作用を達成でき、少量の加圧流体を間欠的に迅速
に供給できる効果がある。O Effects of the Invention Since the present invention is composed of a valve housing and a cylindrical valve body,
The rotary valve structure allows rapid and frequent valve action on pressurized fluid to be achieved, and has the effect of quickly supplying small amounts of pressurized fluid intermittently.
更に、揺動中心設定手段(4)の操作により供給量を簡
単に調節できる効果がある。Furthermore, there is an effect that the supply amount can be easily adjusted by operating the swing center setting means (4).
第1図は本発明の実施例のロータリーバルブを使用した
接着剤塗布機構の要部を示す部分断面図した平面図、第
2図は第1図S−8線による断面図である。
第3図は本発明のロータリーバルブの弁作用を示す略図
、第4図は第3図の弁作用における供給区間と遮断区間
との繰り返しを示す略図、第5図は揺動手段の揺動角の
変化による供給量(塗布量)の変化を示す略図、第6図
は円筒弁体の揺動速度の変化による供給タイミング(!
4!布位置)の変化を示す略図である。
第7図は揺動中心設定手段の作用を示す略図である。
第8図は動力式揺動中心設定手段を示す断面図である。
1・・・・・・弁ハウジング
2・・・・・・円筒弁体
3・・・・・・揺動手段
4・・・・・・揺動中心設定手段
11・・・・・・供給ポート
12・・・・・・吐出ポート
13・・・・・・戻りポート
21・・・・・・弁溝
30・・・・・・駆動軸
出願人 株式会社 サンツール
第2図
X
(a)
劫−’i!F佐1
第7・
SmtlhoJ+= Nt’rJ FIl筒’fru(
z)と弁ハクジングτθの吐出ざ一ト
(12几の肩1月1σ係FIG. 1 is a partially sectional plan view showing essential parts of an adhesive application mechanism using a rotary valve according to an embodiment of the present invention, and FIG. 2 is a sectional view taken along line S-8 in FIG. 1. Fig. 3 is a schematic diagram showing the valve action of the rotary valve of the present invention, Fig. 4 is a schematic diagram showing the repetition of the supply section and cutoff section in the valve action of Fig. 3, and Fig. 5 is the swing angle of the swing means. A schematic diagram showing changes in the supply amount (coating amount) due to changes in .
4! 2 is a schematic diagram showing changes in cloth position). FIG. 7 is a schematic diagram showing the operation of the swing center setting means. FIG. 8 is a sectional view showing the power type swing center setting means. 1... Valve housing 2... Cylindrical valve body 3... Rocking means 4... Rocking center setting means 11... Supply port 12...Discharge port 13...Return port 21...Valve groove 30...Drive shaft applicant Suntool Co., Ltd. Figure 2 X (a) -'i! F Colonel 1 7th SmtlhoJ+= Nt'rJ FIl tube'fru(
z) and the discharge pulse of valve breaking τθ (12 liters of shoulder January 1σ)
Claims (1)
2)と、前記円筒弁体(2)を密封状態で回転自在に支
持するとともに円筒弁体(2)の弁溝(21)と連通可
能な位置に開口した供給ポート(11)、吐出ポート(
12)および戻りポート(13)を有する弁ハウジング
(1)とを設け、円筒弁体(2)を揺動させて、供給ポ
ート(11)と吐出ポート(12)との連通、供給ポー
ト(11)と吐出ポート(12)との遮断を交互に行う
とともに、円筒弁体(2)と揺動手段(3)の駆動軸(
30)とを揺動中心設定手段(4)を介して連結して一
回の揺動に際しての加圧流体の供給時間を変更自在とし
たことを特徴とする加圧流体路のロータリーバルブ。A cylindrical valve body (with a valve groove (21) formed on the circumferential surface of the cylindrical body)
2), a supply port (11) that rotatably supports the cylindrical valve body (2) in a sealed state, and opens at a position where it can communicate with the valve groove (21) of the cylindrical valve body (2), and a discharge port (
A valve housing (1) having a return port (12) and a return port (13) is provided, and the cylindrical valve body (2) is swung to establish communication between the supply port (11) and the discharge port (12), and a return port (13). ) and the discharge port (12) are alternately cut off, and the cylindrical valve body (2) and the drive shaft (
30) via a swing center setting means (4), thereby making it possible to freely change the supply time of pressurized fluid during one swing.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP30254686A JPS63152779A (en) | 1986-12-17 | 1986-12-17 | Rotary valve for pressurized fluid path |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP30254686A JPS63152779A (en) | 1986-12-17 | 1986-12-17 | Rotary valve for pressurized fluid path |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS63152779A true JPS63152779A (en) | 1988-06-25 |
Family
ID=17910267
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP30254686A Pending JPS63152779A (en) | 1986-12-17 | 1986-12-17 | Rotary valve for pressurized fluid path |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS63152779A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102086894A (en) * | 2011-03-28 | 2011-06-08 | 蒋乐庆 | Multi-station full-automatic hydraulic reversing valve |
-
1986
- 1986-12-17 JP JP30254686A patent/JPS63152779A/en active Pending
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102086894A (en) * | 2011-03-28 | 2011-06-08 | 蒋乐庆 | Multi-station full-automatic hydraulic reversing valve |
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