JPS6228581A - Pressure control valve - Google Patents
Pressure control valveInfo
- Publication number
- JPS6228581A JPS6228581A JP16508685A JP16508685A JPS6228581A JP S6228581 A JPS6228581 A JP S6228581A JP 16508685 A JP16508685 A JP 16508685A JP 16508685 A JP16508685 A JP 16508685A JP S6228581 A JPS6228581 A JP S6228581A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- control valve
- spool
- annular groove
- pilot
- 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
- Fluid-Driven Valves (AREA)
- Safety Valves (AREA)
- Control Of Fluid Pressure (AREA)
Abstract
Description
【発明の詳細な説明】
［産業上の利用分野コ
本発明は油圧回路に用いられる圧力制御弁に関するもの
である。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a pressure control valve used in a hydraulic circuit.
［従来の技術］
第３図に示すように、従来の圧力制御弁１は１次側供給
圧力Ｐ１の圧油を供給する入口１６と、２次側出力圧力
Ｐ２を得る出口１７とにそれぞれ連なる環状溝１４．１
５を備えたハウジング２の弁至２２にスプール３が嵌合
され、この反プール３の両端側の！１３．１９はスプー
ル３を貫通するオリフィス通路３Ｃにより連通されると
ともに、スプール３の一端面３ａに室１３のばね４の力
が作用する一方、他端面３ｂに出口１７の圧力が作用す
るように構成される。スプール３には環状溝１４と１５
を連通する幅の広い環状溝１８が設けられる。[Prior Art] As shown in FIG. 3, a conventional pressure control valve 1 is connected to an inlet 16 for supplying pressure oil at a primary side supply pressure P1 and an outlet 17 for obtaining a secondary side output pressure P2. Annular groove 14.1
The spool 3 is fitted into the valve connecting hole 22 of the housing 2, which is provided with the valve 22 of the housing 2, and the spool 3 is fitted on both ends of the opposite side of the spool 3! 13.19 is communicated with by an orifice passage 3C passing through the spool 3, and the force of the spring 4 of the chamber 13 acts on one end surface 3a of the spool 3, while the pressure of the outlet 17 acts on the other end surface 3b. configured. Spool 3 has annular grooves 14 and 15
A wide annular groove 18 is provided that communicates with the two.
圧力制御弁１の端部にパイロブ１−制御弁５が接続され
、ばね７により閉弁方向に付勢されるポペット弁８が、
圧力制御弁１の室１３とヱ１０とを結ぶ通路２１の間に
配設される。ばね７およびポペット弁８はハウジング９
の至１０に収容され、この空１０は通路１２を経てタン
ク２０と接続される。A poppet valve 8 is connected to an end of the pressure control valve 1 with a pyrob 1 and a control valve 5, and is biased in the closing direction by a spring 7.
It is arranged between the passage 21 connecting the chamber 13 of the pressure control valve 1 and the valve 10. Spring 7 and poppet valve 8 are connected to housing 9
This space 10 is connected to a tank 20 via a passage 12.
ダイヤル６によりポペット弁８を開くパイロット圧ＰＣ
ｆｆｉ設定され、オリフィス通路２ａ、 空１９および
オリフィス通路３ｃを経て室１３に作用する２次側圧力
Ｐ２がパイロット圧ｐｃを越えると、パイロット１ｌｌ
ｔｌ弁５のポペット弁８が開き、スプール３の端面３ａ
に作用するパイロット圧ＰＣとばね４の荷重とが、端面
３ｂに作用する２次側圧力Ｐ２と釣合う位置にスプール
３が変位し、入口１６の１次側供給圧力Ｐ１が減圧され
て出口１７にパイロット圧Ｐｃに対応した２次側圧力Ｐ
２ （第４図参照）が得られるようになっている。Pilot pressure PC to open poppet valve 8 by dial 6
ffi is set, and when the secondary pressure P2 acting on the chamber 13 through the orifice passage 2a, the air 19 and the orifice passage 3c exceeds the pilot pressure pc, the pilot 1ll
The poppet valve 8 of the tl valve 5 opens, and the end surface 3a of the spool 3
The spool 3 is displaced to a position where the pilot pressure PC acting on the spring 4 and the load of the spring 4 are balanced with the secondary side pressure P2 acting on the end face 3b, and the primary side supply pressure P1 at the inlet 16 is reduced, and the pressure at the outlet 17 is reduced. The secondary pressure P corresponding to the pilot pressure Pc is
2 (see Figure 4).
この従来技術では、２次側圧力Ｐ２は第４図に線２９．
ｒ−示すように、Ｆ／Ａｏ （ばね４のセット荷！ｌ
Ｆとスプール３の端面３ｂの受圧面積ＡＯとの比）以下
の圧力になり得ない。このため、２次側圧力Ｐ２はＯか
らＦ／ＡＯまでの間の低圧域の制御が不可能である。ま
た、低圧域の制御を行うために、ばね４のセット荷重を
小さくすると、２次側圧力Ｐ２の安定した制御が得られ
なくなる。In this prior art, the secondary pressure P2 is shown as line 29. in FIG.
r - As shown, F/Ao (set load of spring 4! l
The pressure cannot be lower than (the ratio of F to the pressure receiving area AO of the end surface 3b of the spool 3). Therefore, it is impossible to control the secondary side pressure P2 in the low pressure region from O to F/AO. Furthermore, if the set load of the spring 4 is reduced in order to control the low pressure region, stable control of the secondary side pressure P2 cannot be obtained.
［発明が解決しようとする問題点コ
本発明の目的は上述の問題に鑑み、２次側圧力を圧力Ｏ
から所要の圧力まで連続してかつ安定に制御可能な圧力
制御弁を提供することにある。[Problems to be Solved by the Invention] In view of the above-mentioned problems, the purpose of the present invention is to reduce the secondary side pressure to pressure O
The object of the present invention is to provide a pressure control valve that can continuously and stably control the pressure from 1 to a required pressure.
［問題を解決するための手段］
上記目的を達成するために、本発明の構成はポペット型
のパイロット制御弁により所定の圧力に調圧されたパイ
ロット圧によりばねの力に抗して主制御弁のスプールを
開弁方向に変位させ、一次側供給圧力を減圧して所定の
２次側出力圧力を得るようにし、前記パイロット制御弁
のポペット弁と電磁アクチュエータのプランジャとの間
にばねを介装するとともに、前記スプールを前記バイ０
ツト圧を受ける端部が大径である段付きスプールとして
前記段付スプールの小径部にオリフィス通路を設けたも
のである。[Means for solving the problem] In order to achieve the above object, the configuration of the present invention is such that the main control valve is operated against the force of a spring by a pilot pressure regulated to a predetermined pressure by a poppet type pilot control valve. The spool is displaced in the valve opening direction to reduce the primary side supply pressure to obtain a predetermined secondary output pressure, and a spring is interposed between the poppet valve of the pilot control valve and the plunger of the electromagnetic actuator. At the same time, the spool is
The stepped spool is a stepped spool whose end that receives the tightening pressure has a large diameter, and an orifice passage is provided in the small diameter portion of the stepped spool.
［作用］
パイロット制御弁５は常開型の電磁比例減圧弁として作
用し、電磁アクチュエータ２５の励磁電流に応じてプラ
ンジャ３４からばね７の力をポペット弁８に及ぼし、こ
れにより段付きスプール３の端間に作用するパイロット
圧を戻しばね４５の力と釣り合う位ばに変位させる。ば
ね７の力はプランジャ３４の変位量すなわち電磁コイル
６１に加えられる電流にほぼ比例してほぼ直線的に変化
するので、段付きスプール３の上端面に作用するパイロ
ット圧ｐｃは電磁コイル６１の励ｔａ′ＲＷ＆に応じて
直線的に変化し、段付きスプール３もまたパイロット圧
ｐｃに応じて変位し、この変位】が大きくなると減圧比
が低くなり、出口１７の圧力Ｐ２が比例的に低くなる。[Function] The pilot control valve 5 acts as a normally open electromagnetic proportional pressure reducing valve, and applies the force of the spring 7 from the plunger 34 to the poppet valve 8 in accordance with the excitation current of the electromagnetic actuator 25, thereby reducing the pressure of the stepped spool 3. The pilot pressure acting between the ends is displaced to a level that balances the force of the return spring 45. Since the force of the spring 7 changes approximately linearly in proportion to the amount of displacement of the plunger 34, that is, the current applied to the electromagnetic coil 61, the pilot pressure pc acting on the upper end surface of the stepped spool 3 depends on the excitation of the electromagnetic coil 61. The stepped spool 3 is also displaced according to the pilot pressure pc, and as this displacement increases, the pressure reduction ratio decreases and the pressure P2 at the outlet 17 decreases proportionally. .
そこで、励磁電流を連続的に制御することにより、出口
１７の圧力Ｐ２をＯから連続的に増大させることができ
、出口１７の低圧制御が可能となる。Therefore, by continuously controlling the excitation current, the pressure P2 at the outlet 17 can be continuously increased from O, and low pressure control at the outlet 17 becomes possible.
［発明の実施例〕
本発明を実施例に基づいて説明する。第１図に示すよう
に、本発明による圧力制御弁は主制御弁１とパイロット
制御弁５と、これを駆動する電磁アクチュエータ２５と
から構成される。主制御弁１はハウジング２に小径円筒
ｍ２２ａと大径円筒部２２とからなる段付き弁至を備え
ており、これに段付きスプール３が摺動可能に嵌合され
、小径円筒部２２ａの端部には１４４が嵌合され、止め
輪４３により固定される。[Examples of the Invention] The present invention will be described based on Examples. As shown in FIG. 1, the pressure control valve according to the present invention is comprised of a main control valve 1, a pilot control valve 5, and an electromagnetic actuator 25 for driving them. The main control valve 1 is equipped with a stepped valve holder consisting of a small diameter cylinder m22a and a large diameter cylindrical part 22 in a housing 2. A stepped spool 3 is slidably fitted into this, and the end of the small diameter cylindrical part 22a is fitted. 144 is fitted into the portion and fixed by a retaining ring 43.
大径円筒部２２の上端部にはシールリング５０を装着し
たパイロットＩＩＪｔｔｌｌ弁５のハウジング９が嵌合
される。小径円筒部２２ａには環状溝４８が備えられ、
出口４９を経て図示してないタンクと連通される。大径
円筒部２２には環状溝１４と１５が備えられ、環状溝１
４は入口１６を開して油圧ポンプの吐出口と接続され、
環状溝１５は出口１７から圧力作動機器へ接続される。A housing 9 of a pilot II Jttll valve 5 equipped with a seal ring 50 is fitted into the upper end of the large diameter cylindrical portion 22 . The small diameter cylindrical portion 22a is provided with an annular groove 48,
It communicates with a tank (not shown) via an outlet 49. The large diameter cylindrical portion 22 is provided with annular grooves 14 and 15, and the annular groove 1
4 opens the inlet 16 and is connected to the discharge port of the hydraulic pump,
The annular groove 15 is connected from the outlet 17 to pressure-operated equipment.
環状溝１５の両側には円筒部２２よりも僅かに内径が大
きく軸方向の長さが短かい切欠円筒部１５ａが備えられ
る。同様に、環状溝４８の一端側にも切欠円筒部４８ａ
が備えられる。Both sides of the annular groove 15 are provided with cutout cylindrical portions 15a having a slightly larger inner diameter and shorter axial length than the cylindrical portion 22. Similarly, a notched cylindrical portion 48a is also provided on one end side of the annular groove 48.
will be provided.
段付きスプール３は円筒部２２に嵌合する大径軸部に幅
の広い環状溝６０が備えられ、常時環状溝１４と連通ず
る。また、小径軸部に環状溝４１と４２が備えられ、環
状溝４１はこの軸方向移動に伴って環状溝１５を環状溝
４８に連通する状態から環状溝１４に連通ずる状態に切
換わるようになっている。段付きスプール３の下端面に
は割溝４６と円筒部が備えられ、この円筒部と蓋４４と
の間に戻しばね４５が介装される。段付きスプール３の
上端面にも割溝５５が備えられる。The stepped spool 3 is provided with a wide annular groove 60 in its large-diameter shaft portion that fits into the cylindrical portion 22, and is always in communication with the annular groove 14. Further, the small diameter shaft portion is provided with annular grooves 41 and 42, and as the annular groove 41 moves in the axial direction, the annular groove 15 is switched from communicating with the annular groove 48 to communicating with the annular groove 14. It has become. The lower end surface of the stepped spool 3 is provided with a split groove 46 and a cylindrical portion, and a return spring 45 is interposed between the cylindrical portion and the lid 44. A groove 55 is also provided on the upper end surface of the stepped spool 3.
パイロット制御弁５は中空のハウジング９が円筒部２２
の端部に嵌合され、かつ割溝５５を有する段付きスプー
ル３の端面を衝合する４面を備えている。ハウジング９
の上端部はテーパ部と割溝５１を有する大径軸部とを備
えており、これによりハウジング９が軸方向に移動しな
いように固く嵌合固定される。そして、弁室１０の内部
にばね３８に、より開弁方向に付勢されるポペット弁８
が収容され、このボベツ１−弁８の端部に結合したボー
ルが後述するＭｌアクチュエータ２５により通路２１を
閉鎖するようになっている。通路２１は段付きスプール
３の端部に設けたオリフィス通路４０＠経て環状溝１４
と常時連通する。弁室１０はυ１溝５１を経て出口１２
と接続し、さらにタンクに接続される。The pilot control valve 5 has a hollow housing 9 with a cylindrical portion 22.
The stepped spool 3 has four faces that are fitted into the ends of the stepped spool 3 and abut against the end faces of the stepped spool 3 having the grooves 55. housing 9
The upper end portion of the housing 9 is provided with a tapered portion and a large diameter shaft portion having a groove 51, whereby the housing 9 is firmly fitted and fixed so that it does not move in the axial direction. The poppet valve 8 is biased in the valve opening direction by a spring 38 inside the valve chamber 10.
is accommodated, and a ball connected to the end of the valve 1-valve 8 closes the passage 21 by an Ml actuator 25, which will be described later. The passage 21 is connected to the annular groove 14 via an orifice passage 40 provided at the end of the stepped spool 3.
Communicate constantly. The valve chamber 10 passes through the υ1 groove 51 to the outlet 12.
and is further connected to the tank.
電磁アクチュエータ２５はハウジング２の端部に嵌合さ
れ、かつハウジング９の割溝５１を有する端部に押し付
けられた隔壁体５６を備えており、これに非磁性体から
なるスリーブ３７と磁性体からなるスリーブ３７ａとが
結合され、これらは円筒形のコア５９の内部に嵌合支持
される。そして、スリーブ３７．３７ａの内部に通孔３
５を有するプランジャ３４が摺動可能に嵌合され、さら
に端部には鉄心３３が嵌合固定される。The electromagnetic actuator 25 includes a partition 56 that is fitted into the end of the housing 2 and pressed against the end of the housing 9 having the groove 51, and a sleeve 37 made of a non-magnetic material and a partition made of a magnetic material. and a sleeve 37a, which are fitted and supported inside the cylindrical core 59. Then, a through hole 3 is provided inside the sleeve 37.37a.
A plunger 34 having a diameter of 5 is slidably fitted thereinto, and an iron core 33 is fitted and fixed to the end thereof.
コア５９には電磁コイル６１が巻き付けられ、この外側
に円筒形の鉄心５２が嵌合される。さらに、コア５９の
端部に環状の鉄心５８が支持される。そして、鉄心５２
．５８およびスリーブ３７ａの端部に形成したフランジ
は円筒形のハウジング３２の内部に収容され、このハウ
ジング３２から電磁コイル６１の端子導線３１が外方へ
延出されるとともに、カップ型のハウジング３２の開口
端部は隔壁体５６に外■支持される。そして、隔壁体５
Ｇの円筒部においてポペット弁８とプランジャ３４との
間にばね７が介！され、またプランジャ３４と鉄心３３
との間にプランジャ３４のバタ付きを抑えるばね３５が
介装される。An electromagnetic coil 61 is wound around the core 59, and a cylindrical iron core 52 is fitted on the outside of the electromagnetic coil 61. Further, an annular iron core 58 is supported at the end of the core 59 . And iron core 52
．． 58 and the flange formed at the end of the sleeve 37a are housed inside the cylindrical housing 32, from which the terminal conductor 31 of the electromagnetic coil 61 extends outward, and the opening of the cup-shaped housing 32. The end portion is supported externally by the partition wall body 56. And the partition body 5
A spring 7 is interposed between the poppet valve 8 and the plunger 34 in the cylindrical portion of G! Also, the plunger 34 and the iron core 33
A spring 35 is interposed between the plunger 34 and the plunger 34 to prevent the plunger 34 from flapping.
第２図に示すように、ポペット弁８はこの端部に半球形
のくぼみ６２を形成し、これにボール６３を嵌合し、か
つくぼみ６２の縁部６２ａをかしめて一体に結合して構
成される。As shown in FIG. 2, the poppet valve 8 is constructed by forming a hemispherical recess 62 at its end, into which a ball 63 is fitted, and by caulking the edge 62a of the recess 62 and joining them together. be done.
次に、本発明による圧力制御弁の作動について説明する
。電磁アクチュエータ２５の電磁コイル６１が消磁状態
にある時、パイロット制御弁５のポペット弁８はばね３
８の力により押し上げられており、通路２１を開いてい
る。したがって、入口１６から主制御弁１の環状溝１４
へ入った圧油はオリフィス通路４０からυｊ溝５５を有
する段付きスプール３の上端面に油圧を及ぼすと同時に
、通ｉ！８２Ｌ弁室１０．３１Ｊ５１９１１”Ｃ出０１
２からタンクへ戻される。Next, the operation of the pressure control valve according to the present invention will be explained. When the electromagnetic coil 61 of the electromagnetic actuator 25 is in a demagnetized state, the poppet valve 8 of the pilot control valve 5 is activated by the spring 3
8 and opens the passage 21. Therefore, from the inlet 16 to the annular groove 14 of the main control valve 1
The pressure oil that has entered the orifice passage 40 exerts hydraulic pressure on the upper end surface of the stepped spool 3 having the υj groove 55, and at the same time, the pressure oil flows through the i! 82L valve chamber 10.31J51911”C out 01
It is returned to the tank from 2.
段付きスプール３の上端面に作用する油圧により、段付
きスプール３が戻しばね４５の力に抗して押し下げられ
ると、環状溝１４がスプールの環状溝６０により環状溝
１５と連通されると同時に、段付きスプール３の小径軸
部（ランド）が円筒部２２ａへ嵌合して環状溝１５と環
状溝４８との間が遮断される。こうして、入口１６から
環状溝１４へ入った圧油は切欠円筒部１５ａと段付きス
プール３の大径軸部（ランド）とのｌｌｉ問に応じて減
圧されて環状溝１５へ流入し、出口１７から油圧作動機
器へ供給される。When the stepped spool 3 is pushed down against the force of the return spring 45 by the hydraulic pressure acting on the upper end surface of the stepped spool 3, the annular groove 14 is communicated with the annular groove 15 by the annular groove 60 of the spool, and at the same time , the small diameter shaft portion (land) of the stepped spool 3 fits into the cylindrical portion 22a, and the annular groove 15 and the annular groove 48 are cut off. In this way, the pressure oil entering the annular groove 14 from the inlet 16 is reduced in pressure according to the contact between the notched cylindrical portion 15a and the large diameter shaft portion (land) of the stepped spool 3, flows into the annular groove 15, and flows into the annular groove 15, and then flows into the annular groove 15 at the outlet 17. is supplied to hydraulically operated equipment.
段付きスプール３が押し下げられる時、空１９の油は戻
しばね４５を収容する円筒部からこれに連なる径方向の
オリフィス通路５３を経て環状溝４８へ入り、ざらに出
口４９からタンクへ戻される。When the stepped spool 3 is pressed down, the oil in the empty space 19 enters the annular groove 48 from the cylindrical section housing the return spring 45 through the radial orifice passage 53 leading thereto and is returned roughly through the outlet 49 to the tank.
パイロット制御弁５のポペット弁８が通路２１を開いて
いる時、環状溝１４からオリフィス通路４０を経て段付
きスプール３の上端面に及ぼす油圧はごく僅かであるが
、この油圧はポペット弁８が通路２１へ接近されて通路
面積が絞られると、これに比例して増大し、段付きスプ
ール３の下降量が大きくなる。したがつＣ１出口１７の
２次側圧力は比例的に増大する。When the poppet valve 8 of the pilot control valve 5 opens the passage 21, the hydraulic pressure exerted on the upper end surface of the stepped spool 3 from the annular groove 14 through the orifice passage 40 is very small; When the passage 21 is approached and the passage area is narrowed, the passage area increases proportionally, and the amount of descent of the stepped spool 3 increases. Therefore, the secondary pressure at the C1 outlet 17 increases proportionally.
ポペット弁８は１！磁アクチユエータ２５の電磁コイル
６１の電流に比例して下方へ移動される。Poppet valve 8 is 1! It is moved downward in proportion to the current in the electromagnetic coil 61 of the magnetic actuator 25.
すなわち、２４！＆コイル６１が励磁されると、電磁コ
イル６１、隔壁体５６、プランジャ３４、スリーブ５９
、鉄心５８を通る磁界が形成される。In other words, 24! & When the coil 61 is excited, the electromagnetic coil 61, the partition body 56, the plunger 34, and the sleeve 59
, a magnetic field passing through the iron core 58 is formed.
電磁アクチュエータ２５の電磁コイル６１が消磁されて
いる時、ポペット弁８はばね３８の力により押し上げら
れ、通路２１を開いている。したがって、入口１６から
環状溝１４へ入った圧油はオリフィス通路４ｏから通路
２１および弁室１０へ入り、さらに出口１２からタンク
へ流れる。したがって、オリフィス通路４０から削溝５
５を有する段付きスプール３の上端面に作用する油圧は
極く僅かであり、段付きスプール３が下方へ移動しても
、段付きスプール３の大径軸部（ランド〉が円筒部２２
に嵌合したままで環状溝１４と環状溝１５との間が遮断
されているので、出口１７へは圧油が流れず、この圧力
はＯとなる。When the electromagnetic coil 61 of the electromagnetic actuator 25 is demagnetized, the poppet valve 8 is pushed up by the force of the spring 38 and opens the passage 21. Therefore, the pressure oil that enters the annular groove 14 from the inlet 16 enters the passage 21 and the valve chamber 10 from the orifice passage 4o, and further flows from the outlet 12 to the tank. Therefore, from the orifice passage 40 to the groove 5
5, the hydraulic pressure acting on the upper end surface of the stepped spool 3 is extremely small.
Since the annular groove 14 and the annular groove 15 are cut off while they are still fitted, pressure oil does not flow to the outlet 17 and the pressure becomes O.
電磁アクチュエータ２５の電磁コイル６１が励磁される
と、プランジャ３４が励磁電流に応じて下方へ駆動され
、ばね７がボベツ］−弁８を通路２１の方へ押し付ける
力が強くなり通路２１が絞られる。したがって、入口１
６から環状溝１４およびオリフィス通路４０を経て、割
溝５５を有する段付きスプール３の端面に作用する油圧
が高くなり、段付きスプール３が戻しばね４５の力に抗
して下方へ移動する。この段付きスプール３の下方移動
に伴って段付きスプール３の大径軸部（ランド）が環状
溝１５へ移動し、環状溝１４と環状溝１５とが段付きス
プール３の環状溝６０により連通される。この時、小径
円筒部２２ａに段付きスプール３の小径軸部（ランド〉
が眠合し、環状溝１５と環状溝４８との間が遮断される
。しかし、室１９の油は戻しばね４５を支持する円筒部
とオリフィス通路６３を経て環状溝４８へ入り、出口４
９からタンクへ戻される。When the electromagnetic coil 61 of the electromagnetic actuator 25 is excited, the plunger 34 is driven downward in accordance with the exciting current, and the force that presses the spring 7 toward the passage 21 becomes stronger and the passage 21 is narrowed. . Therefore, entrance 1
6, through the annular groove 14 and the orifice passage 40, the hydraulic pressure acting on the end face of the stepped spool 3 having the split groove 55 increases, and the stepped spool 3 moves downward against the force of the return spring 45. As the stepped spool 3 moves downward, the large diameter shaft portion (land) of the stepped spool 3 moves to the annular groove 15, and the annular groove 14 and the annular groove 15 communicate with each other through the annular groove 60 of the stepped spool 3. be done. At this time, the small diameter shaft portion (land) of the stepped spool 3 is attached to the small diameter cylindrical portion 22a.
are asleep, and the annular groove 15 and the annular groove 48 are cut off. However, the oil in the chamber 19 enters the annular groove 48 through the cylindrical section supporting the return spring 45 and the orifice passage 63, and enters the annular groove 48 at the outlet 4.
Returned to the tank from 9.
こうして、入口１６の圧油は環状溝１４、円筒部２２を
経て、環状溝１５から出口１７へ流れる。In this way, the pressure oil at the inlet 16 flows through the annular groove 14 and the cylindrical portion 22 from the annular groove 15 to the outlet 17.
この時の出口１７の圧力は段付きスプール３の上端面に
作用するパイロット圧ｐｃにより決まる。The pressure at the outlet 17 at this time is determined by the pilot pressure pc acting on the upper end surface of the stepped spool 3.
つまり、段付きスプール３の変位に応じて環状溝１５お
よび切欠円筒部４１と、段付きスプール３の大径軸部（
ランド）との隙間に応じて減圧される。In other words, depending on the displacement of the stepped spool 3, the annular groove 15 and the notched cylindrical portion 41 and the large diameter shaft portion (
The pressure is reduced depending on the gap with the land).
［発明の効果］
本発明は上述のように、パイロット制御弁５は常開型の
電磁比例減圧弁として作用し、電磁アクチュエータ２５
の励磁電流に応じてプランジャ３４からばね７の力をポ
ペット弁８に及ぼし、これにより段付きスプール３の端
面に作用するパイロット圧を戻しばね４５の力と釣り合
う位置に変位させる。ばね７の力はプランジャ３４の変
位量すなわち電磁コイル６１に加えられる電流にほぼ比
例してほぼ直線的に変化する。すなわち、段付きスプー
ル３の上端面に作用するパイロット圧ｐｃは電磁コイル
６１の励磁電流に応じて直線的に変化し、段付きスプー
ル３もまたパイロット圧ｐｃに応じて変位し、この変位
量が大きくなると減圧比が低くなり、出口１７の圧力Ｐ
２が比例的に低くなる。すなわち、第４図に実線３０で
示すようにパイロット圧ｐｃの上昇に応じて出口１０の
圧力Ｐ２が上昇する。そこで、励磁電流を連続的に変化
させることにより、出口１７の圧力Ｐ２をＯから連続的
に制御することができ、出口１７の低圧制御が可能とな
る。[Effects of the Invention] As described above, in the present invention, the pilot control valve 5 acts as a normally open electromagnetic proportional pressure reducing valve, and the electromagnetic actuator 25
The force of the spring 7 is exerted from the plunger 34 on the poppet valve 8 in accordance with the excitation current of the plunger 34, thereby displacing the pilot pressure acting on the end face of the stepped spool 3 to a position where it balances the force of the spring 45. The force of the spring 7 changes approximately linearly in approximately proportion to the amount of displacement of the plunger 34, that is, the current applied to the electromagnetic coil 61. That is, the pilot pressure pc acting on the upper end surface of the stepped spool 3 changes linearly in accordance with the excitation current of the electromagnetic coil 61, the stepped spool 3 is also displaced in accordance with the pilot pressure pc, and the amount of this displacement is As the pressure increases, the pressure reduction ratio decreases, and the pressure P at the outlet 17 decreases.
2 will be proportionally lower. That is, as shown by the solid line 30 in FIG. 4, the pressure P2 at the outlet 10 increases as the pilot pressure pc increases. Therefore, by continuously changing the excitation current, the pressure P2 at the outlet 17 can be continuously controlled from O, and low pressure control at the outlet 17 becomes possible.
パイロット圧による段付きスプール３の開弁方向の受圧
面積を出口１７の圧力にょる閉弁方向の受圧面積よりも
大きくしたことにより、小さなパイロット圧により出口
１７の圧力を制御することが可能となり、この結果パイ
ロット制御弁５の小型化および消費電力の節約を図るこ
とができ、さらに主制御弁１の構造の簡略化と小型化を
図ることができる。By making the pressure receiving area of the stepped spool 3 in the valve opening direction due to the pilot pressure larger than the pressure receiving area in the valve closing direction due to the pressure of the outlet 17, it becomes possible to control the pressure of the outlet 17 with a small pilot pressure. As a result, the pilot control valve 5 can be made smaller and power consumption can be reduced, and the structure of the main control valve 1 can be simplified and made smaller.
また、パイロット制御弁５は入口１６の圧力をオリフィ
ス通路４ｏを介して減圧し、これをポペット弁８を経て
タンクへ溢流させてパイロット圧を調整するものである
から、作動が非常に確実でかつパイロット圧の制御性能
が優れている。また、室１９と環状溝１５とにオリフィ
ス通路５３を設けたことにより、電磁コイル６１の励磁
電流が一定の場合にパイロット圧の急激な変化に対して
段付きスプール３の撮動を抑え、これにより入口１６の
圧力変化に対して出口１７の圧力が急激に変化するのを
抑えることができる。In addition, the pilot control valve 5 reduces the pressure at the inlet 16 through the orifice passage 4o, and causes this to overflow into the tank through the poppet valve 8 to adjust the pilot pressure, so its operation is very reliable. Moreover, the pilot pressure control performance is excellent. Further, by providing the orifice passage 53 in the chamber 19 and the annular groove 15, when the excitation current of the electromagnetic coil 61 is constant, the movement of the stepped spool 3 is suppressed in response to a sudden change in pilot pressure. This makes it possible to suppress sudden changes in the pressure at the outlet 17 with respect to changes in the pressure at the inlet 16.
第１図は本発明に係る圧力制御弁の正面断面図、第２図
は同圧力制御弁におけるパイロット制御弁のポペット弁
についての正面断面図、第３図は従来の圧力制御弁の正
面断面図、第４図は従来の圧力制御弁と本発明に係る圧
力制御弁との作用を比較して示す線図である。
１：主制御弁 ２：ハウジング ３：段付きスプール
５ニパイロツト制御弁 ８：ポペット弁９．３２：ハウ
ジング １２，１７，４９：出口１４．１５．４１，４
２．４８．６０＋環状溝１６：入口 ２２．２２ａ：円
筒部 ２５：電磁アクチュエータ ３４ニブランジヤ
４０．５３ニオリフイス通路 ４５：戻しばね ６１：
電磁コイル ６３：ボールFIG. 1 is a front sectional view of a pressure control valve according to the present invention, FIG. 2 is a front sectional view of a poppet valve of a pilot control valve in the same pressure control valve, and FIG. 3 is a front sectional view of a conventional pressure control valve. , FIG. 4 is a diagram comparing and showing the functions of a conventional pressure control valve and a pressure control valve according to the present invention. 1: Main control valve 2: Housing 3: Stepped spool
5 Pilot control valve 8: Poppet valve 9.32: Housing 12, 17, 49: Outlet 14.15.41, 4
2.48.60 + annular groove 16: Inlet 22.22a: Cylindrical part 25: Electromagnetic actuator 34 Nib plunger
40.53 Niorifice passage 45: Return spring 61:
Electromagnetic coil 63: Ball
Claims (1)
されたパイロツト圧によりばねの力に抗して主制御弁の
スプールを開弁方向に変位させ、一次側供給圧力を減圧
して所定の２次側出力圧力を得るようにし、前記パイロ
ツト制御弁のポペツト弁と電磁アクチユエータのプラン
ジヤとの間にばねを介装するとともに、前記スプールを
前記パイロツト圧を受ける端部が大径である段付きスプ
ールとして前記段付スプールの小径部にオリフイス通路
を設けたことを特徴とする圧力制御弁。The pilot pressure regulated to a predetermined pressure by the poppet-type pilot control valve displaces the spool of the main control valve in the opening direction against the force of the spring, reducing the primary supply pressure and increasing the predetermined secondary supply pressure. A spring is interposed between the poppet valve of the pilot control valve and the plunger of the electromagnetic actuator, and the spool is a stepped spool whose end receiving the pilot pressure has a large diameter. A pressure control valve characterized in that an orifice passage is provided in a small diameter portion of the stepped spool.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60165086A JPH0612495B2 (en) | 1985-07-26 | 1985-07-26 | Pressure control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60165086A JPH0612495B2 (en) | 1985-07-26 | 1985-07-26 | Pressure control valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6228581A true JPS6228581A (en) | 1987-02-06 |
| JPH0612495B2 JPH0612495B2 (en) | 1994-02-16 |
Family
ID=15805611
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60165086A Expired - Lifetime JPH0612495B2 (en) | 1985-07-26 | 1985-07-26 | Pressure control valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0612495B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1255044A1 (en) * | 2001-05-02 | 2002-11-06 | Ross Operating Valve Company | Variable pressure control device |
| WO2004109124A1 (en) * | 2003-06-04 | 2004-12-16 | Hydac Fluidtechnik Gmbh | Proportional pressure control valve |
| RU2610768C1 (en) * | 2015-12-31 | 2017-02-15 | Фаат Шигабутдинович Серазетдинов | Regulating pilot valve |
| RU2644002C1 (en) * | 2016-10-25 | 2018-02-06 | Акционерное общество "Научно-производственная фирма "Центральное конструкторское бюро арматуростроения" | Block valve |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50153321A (en) * | 1974-05-31 | 1975-12-10 | ||
| JPS54133630A (en) * | 1978-03-30 | 1979-10-17 | Bosch Gmbh Robert | Pressure regulating valve |
| JPS60129567U (en) * | 1984-02-10 | 1985-08-30 | 株式会社小松製作所 | Solenoid proportional pressure control valve |
-
1985
- 1985-07-26 JP JP60165086A patent/JPH0612495B2/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50153321A (en) * | 1974-05-31 | 1975-12-10 | ||
| JPS54133630A (en) * | 1978-03-30 | 1979-10-17 | Bosch Gmbh Robert | Pressure regulating valve |
| JPS60129567U (en) * | 1984-02-10 | 1985-08-30 | 株式会社小松製作所 | Solenoid proportional pressure control valve |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1255044A1 (en) * | 2001-05-02 | 2002-11-06 | Ross Operating Valve Company | Variable pressure control device |
| WO2004109124A1 (en) * | 2003-06-04 | 2004-12-16 | Hydac Fluidtechnik Gmbh | Proportional pressure control valve |
| JP2006526740A (en) * | 2003-06-04 | 2006-11-24 | ハイダック フルイドテヒニク ゲゼルシャフト ミット ベシュレンクテル ハフツング | Proportional pressure control valve |
| RU2610768C1 (en) * | 2015-12-31 | 2017-02-15 | Фаат Шигабутдинович Серазетдинов | Regulating pilot valve |
| RU2644002C1 (en) * | 2016-10-25 | 2018-02-06 | Акционерное общество "Научно-производственная фирма "Центральное конструкторское бюро арматуростроения" | Block valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0612495B2 (en) | 1994-02-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4744389A (en) | Pressure control device | |
| US4494726A (en) | Control valve | |
| US4785849A (en) | Pressure reducing valve assembly | |
| EP0186167A2 (en) | Electromagnetic directional control valve | |
| US5538026A (en) | Pilot-operated proportional control valve | |
| US3942759A (en) | Magnetically-actuated membrane valve | |
| US5529387A (en) | Solenoid operated discharging orifice shutoff valve | |
| US4971114A (en) | Electromagnetic proportional pressure control valve | |
| US4875501A (en) | Electromagnetic proportional control valve apparatus | |
| US6161585A (en) | High flow proportional pressure reducing valve | |
| JPH084937A (en) | Fluid control valve | |
| KR100476246B1 (en) | Proportional pressure control valve | |
| JPS6228581A (en) | Pressure control valve | |
| JPS62261782A (en) | Electromagnetic proportional pressure control valve | |
| JP2006083879A (en) | Solenoid valve | |
| JPH0150794B2 (en) | ||
| JPH01261581A (en) | Control valve | |
| JPH0341179Y2 (en) | ||
| JPH0246384A (en) | Solenoid valve | |
| JPH02138583A (en) | Solenoid valve | |
| JP2000120911A (en) | Solenoid valve | |
| JPH06117566A (en) | Proportional solenoid valve | |
| JPS6298409A (en) | Electromagnetic proportional pressure control valve | |
| JPS61149676A (en) | Pressure control valve | |
| JPH0535445B2 (en) |