JPH0893961A - Hysteresis valve device - Google Patents
Hysteresis valve deviceInfo
- Publication number
- JPH0893961A JPH0893961A JP6224967A JP22496794A JPH0893961A JP H0893961 A JPH0893961 A JP H0893961A JP 6224967 A JP6224967 A JP 6224967A JP 22496794 A JP22496794 A JP 22496794A JP H0893961 A JPH0893961 A JP H0893961A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- pressing force
- piston
- spring
- side chamber
- 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
- 238000003825 pressing Methods 0.000 claims abstract description 62
- 239000012530 fluid Substances 0.000 claims abstract description 44
- 238000010586 diagram Methods 0.000 description 8
- 230000007423 decrease Effects 0.000 description 7
- 238000004519 manufacturing process Methods 0.000 description 4
- 230000003247 decreasing effect Effects 0.000 description 3
- 230000000630 rising effect Effects 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
Landscapes
- Fluid-Driven Valves (AREA)
- Safety Valves (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、油圧モータの吐出制御
装置や油圧バルブ、油圧ブレーキ等の各種油圧装置を制
御する制御パイロット流体の圧力の上昇時と下降時に於
いて差異を生じさせるヒステリシスバルブ装置に関す
る。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hysteresis valve for producing a difference between a pressure rise and a pressure drop of a control pilot fluid for controlling various hydraulic devices such as a discharge control device of a hydraulic motor, a hydraulic valve, and a hydraulic brake. Regarding the device.
【０００２】[0002]
【従来の技術】従来、この種のバルブとして、例えば図
１に示すように、パイロット流体の導入口ａと制御パイ
ロット流体の導出口ｂ及びタンク口ｃを備えたケーシン
グｄ内に、一端にばねｅによる押圧力が作用し他端に片
ロッド形のピストンｆの押圧力が作用したスプール弁ｇ
を設け、該スプール弁ｇは、該導入口ａ、導出口ｂ及び
該ピストンｆのヘッド側室ｈを相互に接続する第１位置
と、該導出口ｂ及び該ピストンｆのロッド側室ｉをタン
クｊへ接続すると共に該導入口ａと該ヘッド側室ｈを接
続する第２位置とに移動可能に構成したものが知られて
いる（実開昭６１−２０４００４号公報）。2. Description of the Related Art Conventionally, as a valve of this type, for example, as shown in FIG. 1, a spring is provided at one end in a casing d having a pilot fluid inlet port a, a control pilot fluid outlet port b, and a tank port c. spool valve g in which the pressing force of e is applied and the pressing force of the single rod type piston f is applied to the other end
The spool valve g connects the inlet port a, the outlet port b and the head side chamber h of the piston f to each other, and the outlet port b and the rod side chamber i of the piston f to the tank j. There is known a structure in which it is movable to a second position where the inlet a and the head side chamber h are connected to each other while being connected to the above (Japanese Utility Model Publication No. 61-204004).
【０００３】このバルブは、スプール弁ｇが第１位置に
あるときは、ピストンｆのヘッド側室ｈとロッド側室ｉ
とに受圧面積の差があるため、導出口ｂには大きな圧力
の制御パイロット流体が得られ、該ピストンｆに発生す
る推力がばねｅの力を越えると該スプール弁ｇは第２位
置に切換わり、このときはピストンｆに推力を発生させ
る受圧面積がヘッド側室ｈの面積のみであるので、導入
口ａに作用するパイロット流体の圧力が第１位置から第
２位置へ切換わったときの圧力よりも相当低くならない
と第１位置へ復帰しないようになり、導出口ｂにはパイ
ロット流体の圧力上昇時と下降時とで異なったヒステリ
シス形の制御パイロット圧力が得られる。図示のよう
に、導出口ｂへ可変油圧モータの容量制御装置の制御シ
リンダｋを接続した場合、該スプール弁ｇが図示の第１
位置にあると、導入口ａにかなり高い圧力のパイロット
流体を導入して該制御シリンダｋをモータ吐出量を減少
側へ押し、モータ吐出量の増大側へは該パイロット流体
がかなり低い圧力にならないと移動しないように制御す
ることができる。This valve has a head side chamber h and a rod side chamber i of the piston f when the spool valve g is in the first position.
Since there is a difference in the pressure receiving area between and, a large pressure control pilot fluid is obtained at the outlet b, and when the thrust generated in the piston f exceeds the force of the spring e, the spool valve g is switched to the second position. At this time, since the pressure receiving area for generating the thrust on the piston f is only the area of the head side chamber h, the pressure when the pilot fluid pressure acting on the inlet a is switched from the first position to the second position. If the pressure is not much lower than that, it will not return to the first position, and a different hysteresis type control pilot pressure is obtained at the outlet b when the pressure of the pilot fluid rises and when it falls. As shown in the drawing, when the control cylinder k of the displacement control device of the variable hydraulic motor is connected to the outlet b, the spool valve g is
In the position, the pilot fluid having a considerably high pressure is introduced into the inlet a to push the control cylinder k to the motor discharge amount decreasing side, and the pilot fluid does not have a considerably low pressure to the motor discharge amount increasing side. And can be controlled not to move.
【０００４】また、図２に示すような回転体ｌの油圧ブ
レーキ装置ｍを単にパイロットラインｎに作用するパイ
ロット流体の圧力で制御した場合、そのパイロット流体
の圧力を上げると該装置ｍはその内部のばねが撓んで該
回転体ｌのブレーキが解除され、その圧力を下げると該
ばねによりブレーキが掛かり、パイロット流体の圧力Ｐ
P とブレーキ力の関係は図３のようにパイロット流体の
圧力の昇降時に同一直線となるが、パイロットラインｎ
にヒステリシスバルブｏを介在させると、図４に示すよ
うなパイロット流体の圧力上昇時と下降時とで異なるブ
レーキ力が得られる。図４のようなブレーキ特性が得ら
れると、回転体ｌの加速時よりも減速時にブレーキ力を
大きくすることができ、パイロット流体の圧力の応答遅
れによるブレーキ解放時のつれ回りが解消され、減速時
のブレーキ力不足を解消して緊急停止時の信頼性が向上
する。Further, when the hydraulic brake device m of the rotating body 1 as shown in FIG. 2 is controlled only by the pressure of the pilot fluid acting on the pilot line n, when the pressure of the pilot fluid is increased, the device m is internally operated. When the pressure of the rotary body 1 is released by releasing the brake of the spring, the brake is applied by the spring, and the pressure P of the pilot fluid is increased.
The relationship between P and the braking force becomes the same straight line when the pressure of the pilot fluid rises and falls as shown in FIG.
By interposing the hysteresis valve o in the above, different braking force can be obtained when the pressure of the pilot fluid rises and when it falls as shown in FIG. When the braking characteristic as shown in FIG. 4 is obtained, the braking force can be made larger during deceleration than during acceleration of the rotating body l, and the whirling at the time of brake release due to the response delay of the pressure of the pilot fluid is eliminated, resulting in deceleration Insufficient braking force is eliminated to improve reliability during an emergency stop.
【０００５】[0005]
【発明が解決しようとする課題】このようなヒステリシ
スバルブを実際の油圧装置、例えば可変形油圧モータの
容量制御装置、油圧回路の圧力制御装置に使用した場
合、その油圧装置に適した制御フィーリングに調整する
ため或いは製作誤差の補正のためにヒステリシス幅を変
更することの要望が存する。When such a hysteresis valve is used in an actual hydraulic system such as a displacement control system for a variable hydraulic motor or a pressure control system for a hydraulic circuit, a control feeling suitable for the hydraulic system is obtained. There is a demand to change the hysteresis width in order to adjust to the above or to correct the manufacturing error.
【０００６】本発明は、こうした要望を満足すべく自在
にヒステリシス幅を調整できるヒステリシスバルブを提
供することを目的とするものである。An object of the present invention is to provide a hysteresis valve whose hysteresis width can be adjusted freely to satisfy such demands.
【０００７】[0007]
【課題を解決するための手段】本発明では、圧力が変化
するパイロット流体の導入口と制御パイロット流体の導
出口及びタンク口を備えたケーシング内に、一端にばね
による押圧力が作用し他端に片ロッド形のピストンの押
圧力が作用したスプール弁を設け、該スプール弁は、該
ばねの押圧力が該ピストンの押圧力よりも優勢のとき
に、該導入口、導出口、該ピストンのロッド側室及びヘ
ッド側室を相互に接続する第１位置と、該ピストンの押
圧力が該ばねの押圧力よりも優勢のときに、該ロッド側
室とタンク口を接続すると共に該導入口と該導出口をシ
ーケンス弁及び該スプール弁を介して接続し、且つ該ヘ
ッド側室を該導入口に接続する第２位置の切換位置を有
することにより、また、圧力が変化するパイロット流体
の導入口と制御パイロット流体の導出口及びタンク口を
備えたケーシング内に、一端にばねによる押圧力が作用
し他端に片ロッド形のピストンの押圧力が作用したスプ
ール弁を設け、該スプール弁が、該ばねの押圧力が該ピ
ストンの押圧力よりも優勢のときに、該導入口をシーケ
ンス弁を介して導出口、該ピストンのロッド側室及びヘ
ッド側室に接続する第１位置と、該ピストンの押圧力が
該ばねの押圧力よりも優勢のときに、該ロッド側室とタ
ンク口を接続すると共に該導出口と該導入口及び該ヘッ
ド側室を相互に接続する第２位置の切換位置を有するこ
とにより、上記の目的を達成するようにした。According to the present invention, a pressing force by a spring acts on one end of a casing having a pilot fluid inlet for changing pressure, an outlet for control pilot fluid, and a tank, and the other end A spool valve to which a pressing force of a piston of a single rod type is applied is provided in the spool valve. When the pressing force of the spring is superior to the pressing force of the piston, the spool valve is provided with the inlet port, the outlet port, and the piston port. A first position for connecting the rod side chamber and the head side chamber to each other, and when the pressing force of the piston is superior to the pressing force of the spring, the rod side chamber is connected to the tank port and the inlet port and the outlet port are connected. Is connected via a sequence valve and the spool valve, and has a switching position of a second position for connecting the head side chamber to the introduction port. A spool valve, in which a pressing force of a spring acts on one end and a pushing force of a one-rod-type piston acts on the other end, is provided in a casing having a discharge port and a tank port for the outlet fluid. When the pressing force of the spring is more dominant than the pressing force of the piston, a first position connecting the inlet port to the outlet port through the sequence valve, the rod side chamber and the head side chamber of the piston, and the pressing force of the piston Has a switching position of a second position for connecting the rod side chamber and the tank port and interconnecting the outlet port, the inlet port and the head side chamber, when is superior to the pressing force of the spring, The above-mentioned purpose is achieved.
【０００８】[0008]
【作用】請求項１の構成の場合、パイロット流体の圧力
ＰP により片ロッド形のピストンに発生する押圧力がス
プール弁のばねの押圧力よりも小さい領域では、該スプ
ール弁は第１位置に存し、導入口のパイロット流体の圧
力がそのまま導出口から導出される。従ってパイロット
流体の圧力ＰP が上昇すれば、これと同圧が図６のよう
に該導出口に得られ、該導出口に接続された例えば油圧
ブレーキにそのまま上昇圧を作用させることができる。
該パイロット流体の圧力ＰP が上昇して該ピストンの押
圧力がスプール弁の押圧力を越えると、スプール弁は第
２位置へ移動し、導入口の圧力ＰX はシーケンス弁で制
御されて低下したパイロット流体の圧力ＰP −ΔＰとな
る。一方、該ピストンのロッド側室はタンクへ接続さ
れ、ヘッド側室には上昇したパイロット流体の圧力ＰP
が作用するので、この第２位置は保持される。従って、
この第２位置にスプール弁が切換わることにより、導出
口の圧力ＰX は一時的にその切換わり前よりも低い圧力
となるが、その第２位置は保持されるので、該パイロッ
ト流体の圧力が上昇を続ければ再び切換わり前の圧力を
越えて上昇するようになる。この状態から該パイロット
流体の圧力ＰP を低下させると、該導出口の圧力ＰX も
そのまま低下し、該ピストンの押圧力がばねの押圧力以
下になると、スプール弁は第１位置に戻ることになる
が、ピストンの受圧面積は第２位置の時の方が第１位置
のときよりも大きいので、第１位置から第２位置に切換
わるときよりも低い圧力にならないと第２位置から第１
位置への切換わらない。そして第２位置へ切換わったの
ちは、導出口の圧力はパイロット流体の圧力と同圧にな
り、パイロット流体と同じ圧力で低下し、図６のような
パイロット流体の上昇時と下降時とでヒステリシスを持
つ圧力変化が導出口に得られる。このヒステリシスの圧
力差ΔＰは、シーケンス弁により自在に調整することが
出来るから、導出口に接続した油圧機器を任意のヒステ
リシス幅で制御することが出来る。According to the first aspect of the invention, the spool valve is set to the first position in the region where the pressing force generated on the one rod type piston by the pilot fluid pressure P P is smaller than the pressing force of the spring of the spool valve. The pressure of the pilot fluid at the inlet is discharged as it is from the outlet. Therefore, if the pressure P P of the pilot fluid increases, the same pressure as this is obtained at the outlet as shown in FIG. 6, and the increased pressure can be directly applied to, for example, a hydraulic brake connected to the outlet.
When the pressure P P of the pilot fluid increases and the pressing force of the piston exceeds the pressing force of the spool valve, the spool valve moves to the second position, and the pressure P X at the inlet is controlled by the sequence valve and decreases. The pressure of the pilot fluid is P P −ΔP. On the other hand, the rod side chamber of the piston is connected to the tank, and the head side chamber has a pressure P P of the raised pilot fluid.
, The second position is retained. Therefore,
By switching the spool valve to the second position, the pressure P X at the outlet becomes temporarily lower than that before switching, but since the second position is maintained, the pressure of the pilot fluid is maintained. If the pressure continues to rise, the pressure again rises above the pressure before switching. When the pressure P P of the pilot fluid is decreased from this state, the pressure P X of the outlet is also decreased, and when the pressing force of the piston becomes equal to or lower than the pressing force of the spring, the spool valve returns to the first position. However, since the pressure receiving area of the piston is larger in the second position than in the first position, the pressure from the second position must be lower than that when switching from the first position to the second position. 1
Does not switch to the position. After switching to the second position, the pressure at the outlet becomes the same as the pressure of the pilot fluid and decreases at the same pressure as the pilot fluid. When the pilot fluid rises and falls as shown in FIG. A pressure change with hysteresis is obtained at the outlet. Since the pressure difference ΔP of the hysteresis can be freely adjusted by the sequence valve, the hydraulic device connected to the outlet can be controlled with an arbitrary hysteresis width.
【０００９】また、請求項２の構成の場合、スプール弁
の第１位置では導入口からのパイロット流体がシーケン
ス弁を介して導出口とピストンのヘッド側及びロッド側
に導かれ、第２位置では導入口が導出口とヘッド側室に
接続されると共にロッド側室がタンク口に接続され点が
請求項１の構成と相違する。この場合、該ピストンに発
生する押圧力がスプール弁のばねの押圧力よりも小さい
領域では、導出口からはシーケンス弁により減圧された
圧力が得られ、該ピストンに発生する押圧力がスプール
弁のばねの押圧力よりも大きい領域では、導出口に導入
口と同圧が得られる。従って、導入口のパイロット流体
の圧力が上昇する過程に於いては、途中までシーケンス
弁で減圧された圧力が導出口に導出され、第２位置に切
換わったときから導入口と同圧の流体が導出口に導出さ
れ、更に、導入口のパイロット流体の圧力が下降する過
程に於いては、第１位置に切換わるとシーケンス弁で減
圧された圧力が導出口の圧力になり、圧力上昇時よりも
圧力下降時の圧力が高いヒステリシスの圧力変化が得ら
れる。この場合もシーケンス弁でヒステリシス幅を調整
できる。Further, in the structure of claim 2, in the first position of the spool valve, the pilot fluid from the inlet is guided to the outlet and the head side and rod side of the piston through the sequence valve, and in the second position. It differs from the configuration of claim 1 in that the inlet is connected to the outlet and the head side chamber and the rod side chamber is connected to the tank port. In this case, in the region where the pressing force generated on the piston is smaller than the pressing force of the spring of the spool valve, the pressure reduced by the sequence valve is obtained from the outlet, and the pressing force generated on the piston is In a region larger than the pressing force of the spring, the same pressure as that of the introduction port can be obtained at the outlet port. Therefore, in the process in which the pressure of the pilot fluid in the inlet increases, the pressure partially reduced by the sequence valve is led to the outlet, and the fluid having the same pressure as the inlet from the time of switching to the second position. In the process in which the pressure of the pilot fluid at the inlet is lowered and the pressure of the pilot fluid at the inlet is switched to the first position, the pressure reduced by the sequence valve becomes the pressure at the outlet, and when the pressure rises. A hysteresis pressure change is obtained in which the pressure when the pressure decreases is higher than that. In this case as well, the hysteresis width can be adjusted with the sequence valve.
【００１０】[0010]
【実施例】本発明の実施例を図面に基づき説明すると、
図５に於いて、符号１はパイロット流体の導入口２と制
御パイロット流体の導出口３及びタンク口４を備えたケ
ーシングを示し、該ケーシング１の内部に、一端にばね
５の押圧力が作用すると共に他端に片ロッド形のピスト
ン６の押圧力が作用したスプール弁７が設けられる。該
スプール弁７は、該ばね５の押圧力が該ピストン６に発
生する押圧力よりも大きいときは第１位置７ａに存し、
該ばね５の押圧力が該ピストン６に発生する押圧力より
も小さいときは第２位置７ｂに位置するもので、その第
１位置７ａに於いては、その導入口２と導出口３、該ピ
ストン６のヘッド側室６ａ、及びロッド側室６ｂを相互
に接続し、その第２位置に於いては、導入口２をシーケ
ンス弁８及びスプール弁７を介して導出口３へ接続する
と共にロッド側室６ｂをタンク口４に接続し、ヘッド側
室６ｂは変りなく導入口２へ接続するように構成され
る。尚、ピストン６はそのヘッド側室６ａとロッド側室
６ｂの受圧面積が異なっているため、両室に同圧が作用
したときはそのロッドはスプール弁７を押圧する。該ば
ね５はばね力を調整ナット等により調整可能に設けられ
る。Embodiments of the present invention will be described with reference to the drawings.
In FIG. 5, reference numeral 1 denotes a casing provided with a pilot fluid inlet port 2, a control pilot fluid outlet port 3 and a tank port 4. Inside the casing 1, a pressing force of a spring 5 acts at one end. In addition, a spool valve 7 to which the pressing force of the one rod type piston 6 acts is provided at the other end. The spool valve 7 is in the first position 7a when the pressing force of the spring 5 is larger than the pressing force generated in the piston 6,
When the pressing force of the spring 5 is smaller than the pressing force generated by the piston 6, the spring 5 is located at the second position 7b. At the first position 7a, the inlet 2 and the outlet 3, The head side chamber 6a and the rod side chamber 6b of the piston 6 are connected to each other, and in the second position thereof, the inlet port 2 is connected to the outlet port 3 via the sequence valve 8 and the spool valve 7 and the rod side chamber 6b is connected. Is connected to the tank port 4, and the head side chamber 6b is connected to the inlet port 2 without change. Since the pressure receiving areas of the head side chamber 6a and the rod side chamber 6b of the piston 6 are different, the rod presses the spool valve 7 when the same pressure acts on both chambers. The spring 5 is provided so that the spring force can be adjusted by an adjusting nut or the like.
【００１１】該導入口２には、圧力制御弁により圧力の
昇降が自在に制御されたパイロット流体を供給する油圧
源が接続され、該導出口３には、例えば図２に示すよう
な油圧ブレーキが接続される。この場合、該油圧ブレー
キを早めに解除し、早めにブレーキを掛けることがで
き、該油圧源から導入口２に供給されるパイロット流体
の圧力を比較的低い圧力から上昇させると、スプール弁
７は第１位置７ａに位置し、上昇する導入口２の圧力が
そのまま導出口３の圧力になるから、図６のように、導
入口２と同じ上昇する圧力が導出され、例えば油圧ブレ
ーキを油圧源の圧力上昇に応じて解除することができ
る。該導入口２の圧力が上昇してピストン６に発生する
押圧力が大きくなり、スプール弁７が第２位置７ｂへ切
換わると、導出口３からはシーケンス弁８を介して導入
口２からのパイロット流体が導出され、該シーケンス弁
８の機能により導出口３の圧力は一旦低下し、その後、
導入口２の圧力上昇につれて上昇するから、過剰な油圧
ブレーキの解放作動は少なくなる。解放していた油圧ブ
レーキに制動を行わせる場合、該油圧源の圧力を降下さ
せ導入口２の圧力を降下させるが、この場合はその圧力
降下の割合に応じてシーケンス弁８に制御されながら導
出口３の圧力が降下するので、ブレーキの利きが早く、
該導入口２の圧力により発生するピストン６の押圧力が
ばね５のばね力以下になると、該スプール弁７が第１位
置７ａに戻り、このときシーケンス弁８の介入が除外さ
れるので、導出口３は導入口２と直結し、その圧力は一
旦上昇するがそれ以後は該油圧源の圧力降下に応じて降
下する。A hydraulic pressure source for supplying a pilot fluid whose pressure can be freely raised and lowered by a pressure control valve is connected to the inlet port 2, and a hydraulic brake as shown in FIG. 2 is connected to the outlet port 3. Are connected. In this case, the hydraulic brake can be released early and the brake can be applied early, and when the pressure of the pilot fluid supplied from the hydraulic source to the inlet 2 is increased from a relatively low pressure, the spool valve 7 Since the pressure of the inlet port 2 located at the first position 7a and rising is the pressure of the outlet port 3 as it is, the same rising pressure as that of the inlet port 2 is derived as shown in FIG. It can be released according to the increase in pressure. When the pressure of the inlet port 2 rises and the pressing force generated in the piston 6 increases, and the spool valve 7 switches to the second position 7b, the outlet port 3 passes through the sequence valve 8 and the inlet port 2 passes through. The pilot fluid is discharged, the pressure of the discharge port 3 is once reduced by the function of the sequence valve 8, and then,
Since the pressure rises as the pressure of the inlet 2 increases, the excessive hydraulic brake release operation decreases. When the released hydraulic brake is to be braked, the pressure of the hydraulic source is lowered and the pressure of the inlet 2 is lowered. In this case, the sequence valve 8 is controlled according to the rate of the pressure drop. Since the pressure at the outlet 3 drops, the brake will work quickly,
When the pressing force of the piston 6 generated by the pressure of the introduction port 2 becomes equal to or less than the spring force of the spring 5, the spool valve 7 returns to the first position 7a, and the intervention of the sequence valve 8 is excluded at this time. The outlet 3 is directly connected to the inlet 2, and its pressure rises once, but thereafter it drops according to the pressure drop of the hydraulic pressure source.
【００１２】図７の例は、該スプール弁７の切換位置
を、該ばね５の押圧力が該ピストン６の押圧力よりも優
勢のときに、該導入口２をシーケンス弁８を介して導出
口３、該ピストン６のロッド側室６ｂ及びヘッド側室６
ａに接続する第１位置９ａと、該ピストン６の押圧力が
該ばね５の押圧力よりも優勢のときに、該ロッド側室６
ｂとタンク口４を接続すると共に該導出口３と該導入口
２及び該ヘッド側室６ａを相互に接続する第２位置９ｂ
とで構成したもので、この場合も該導入口２に油圧源を
接続し、導出口３に例えば油圧ブレーキを接続すれば、
該油圧源の圧力の昇降で図８のようなヒステリシス制御
を行える。即ち、油圧源が低圧から圧力上昇する時には
該ばね５の力がピストン６の押圧力よりも優勢でシーケ
ンス弁８が介入する第１位置９ａにあるので、図８のよ
うに、導出口３の圧力は減圧されながら上昇し、該ピス
トン６の押圧力がばね５の力よりも優勢になったところ
でシーケンス弁８が除外される第２位置９ｂに切換わ
り、それ以後は一段圧力が高くなった状態で昇圧を続け
る。該油圧源が高圧から低下するときは、そのまま低下
し、ピストン６の押圧力がばね５の力よりも優勢になっ
たところでシーケンス弁８が介入する第１位置９ａに切
換わるので、一段低くなった状態で圧力低下が進む。こ
の場合、例えば導出口３に図３の油圧ブレーキが設けら
れていると、これを徐々に解除し、急激にブレーキを掛
けることができる。In the example of FIG. 7, the switching position of the spool valve 7 is guided through the introduction valve 2 through the sequence valve 8 when the pressing force of the spring 5 is superior to the pressing force of the piston 6. Outlet 3, rod side chamber 6b of piston 6 and head side chamber 6
When the pressing force of the piston 6 is superior to the pressing force of the spring 5 and the first position 9a connected to a, the rod side chamber 6
Second position 9b for connecting b to the tank port 4 and interconnecting the outlet port 3, the inlet port 2 and the head side chamber 6a.
In this case also, if a hydraulic pressure source is connected to the inlet 2 and a hydraulic brake is connected to the outlet 3, for example,
Hysteresis control as shown in FIG. 8 can be performed by raising or lowering the pressure of the hydraulic pressure source. That is, since the force of the spring 5 is more dominant than the pressing force of the piston 6 and the sequence valve 8 is in the first position 9a where the sequence valve 8 intervenes when the pressure of the hydraulic pressure source rises from the low pressure, as shown in FIG. The pressure is increased while being reduced, and when the pressing force of the piston 6 becomes more dominant than the force of the spring 5, the sequence valve 8 is switched to the second position 9b where it is excluded, and thereafter the pressure is increased by one step. Continue boosting in the state. When the hydraulic pressure source decreases from high pressure, it decreases as it is, and when the pressing force of the piston 6 becomes more dominant than the force of the spring 5, the sequence valve 8 switches to the first position 9a where it intervenes, so it decreases one step further. The pressure drop progresses in the closed state. In this case, for example, if the hydraulic brake shown in FIG. 3 is provided at the outlet 3, the hydraulic brake can be gradually released and the brake can be suddenly applied.
【００１３】該シーケンス弁８は、圧力降下特性の調整
が自在のものであることが好ましく、これを調整するこ
とによりヒステリシス幅ΔＰを任意に設定できる。ま
た、ヒステリシス発生圧力Ｐ１またはＰ２は、スプール
弁７のばね５のばね力を変更することにより設定を変更
でき、Ｐ１とＰ２の比はピストン６のヘッド側室６ａと
ロッド側室６ｂの受圧面積の比を変えることにより変更
できる。従って、受圧面積の変更以外は、導出口３に接
続した油圧機器のフィーリングなどに合せてシーケンス
弁８やばね５の調整が可能で、効率良く設定できる。ま
た、ヒステリシスバルブ自体に製造誤差がある場合の補
正もその調整により行えるので、品質が向上する。更
に、本ヒステリシスバルブは、既存の油圧機器の制御ラ
インに追加することができ、既存の油圧機器の機能向上
を容易に計れる。It is preferable that the pressure drop characteristic of the sequence valve 8 can be freely adjusted, and the hysteresis width ΔP can be arbitrarily set by adjusting the pressure drop characteristic. Further, the hysteresis generation pressure P1 or P2 can be set by changing the spring force of the spring 5 of the spool valve 7, and the ratio of P1 and P2 is the ratio of the pressure receiving area of the head side chamber 6a of the piston 6 to the rod side chamber 6b. It can be changed by changing. Therefore, other than changing the pressure receiving area, the sequence valve 8 and the spring 5 can be adjusted according to the feeling of the hydraulic equipment connected to the outlet 3, and the setting can be made efficiently. In addition, since the correction can be performed when the hysteresis valve itself has a manufacturing error by the adjustment, the quality is improved. Furthermore, this hysteresis valve can be added to the control line of the existing hydraulic equipment, and the function of the existing hydraulic equipment can be easily improved.
【００１４】[0014]
【発明の効果】以上のように、請求項１の発明によれ
ば、一端にばねによる押圧力が作用し他端に片ロッド形
のピストンの押圧力が作用したスプール弁をケーシング
内に設け、該スプール弁は、該ばねの押圧力が該ピスト
ンの押圧力よりも優勢のときに、該ケーシングの導入
口、導出口、該ピストンのロッド側室及びヘッド側室を
相互に接続する第１位置と、該ピストンの押圧力が該ば
ねの押圧力よりも優勢のときに、該ロッド側室とタンク
口を接続すると共に該導入口と該導出口をシーケンス弁
及び該スプール弁を介して接続し、且つ該ヘッド側室を
該導入口に接続する第２位置の切換位置を有するので、
該導入口に作用する圧力の上昇時よりもその下降時の圧
力の低いヒステリシス制御を行え、該ばねのばね力やシ
ーケンス弁の設定を変更することにより簡単にしかも自
在にヒステリシス幅を調整できて便利であり、ヒステリ
シスバルブ自体の製造誤差の補正も行えるので品質も良
好で、既存のラインに簡単に取り付けできる等の効果が
得られ、また、請求項２の発明によれば、一端にばねに
よる押圧力が作用し他端に片ロッド形のピストンの押圧
力が作用したスプール弁をケーシング内に設け、該スプ
ール弁は、該ばねの押圧力が該ピストンの押圧力よりも
優勢のときに、該ケーシングの導入口をシーケンス弁を
介して導出口、該ピストンのロッド側室及びヘッド側室
に接続する第１位置と、該ピストンの押圧力が該ばねの
押圧力よりも優勢のときに、該ロッド側室とタンク口を
接続すると共に該導出口と該導入口及び該ヘッド側室を
相互に接続する第２位置の切換位置を有するので、該導
入口に作用する圧力の上昇時よりもその下降時の圧力が
高いヒステリシス制御を行え、請求項１の場合と同様に
該ばねのばね力やシーケンス弁の設定を変更することに
より簡単にしかも自在にヒステリシス幅を調整できて便
利であり、ヒステリシスバルブ自体の製造誤差の補正も
行えるので品質も良好で、既存のラインに簡単に取り付
けできる等の効果が得られる。As described above, according to the first aspect of the present invention, the spool valve, in which the pressing force of the spring acts on one end and the pushing force of the single rod type piston acts on the other end, is provided in the casing. The spool valve has a first position connecting the inlet port, the outlet port of the casing, the rod side chamber and the head side chamber of the piston to each other when the pressing force of the spring is superior to the pressing force of the piston; When the pressing force of the piston is superior to the pressing force of the spring, the rod side chamber is connected to the tank port, the inlet port and the outlet port are connected via a sequence valve and the spool valve, and Since it has the switching position of the second position that connects the head side chamber to the inlet,
Hysteresis control in which the pressure acting on the inlet is lower than when the pressure is rising can be performed, and the hysteresis width can be easily and freely adjusted by changing the spring force of the spring or the setting of the sequence valve. It is convenient, and the manufacturing error of the hysteresis valve itself can be corrected, so that the quality is good and the effect that it can be easily attached to the existing line can be obtained. Further, according to the invention of claim 2, a spring is provided at one end. A spool valve, to which the pressing force acts and the pushing force of the one rod type piston acts on the other end, is provided in the casing, and the spool valve is configured such that when the pressing force of the spring is higher than the pressing force of the piston, A first position connecting the inlet of the casing to the outlet via a sequence valve, the rod side chamber and the head side chamber of the piston, and the pressing force of the piston is superior to the pressing force of the spring. At this time, since there is a switching position of the second position for connecting the rod side chamber and the tank port and interconnecting the outlet port, the introduction port and the head side chamber, Also, the hysteresis pressure with a high pressure when descending can be performed, and it is convenient that the hysteresis width can be easily and freely adjusted by changing the spring force of the spring and the setting of the sequence valve as in the case of claim 1. Since the manufacturing error of the hysteresis valve itself can be corrected, the quality is good, and the effect that it can be easily attached to the existing line can be obtained.
【図１】 従来例の説明線図FIG. 1 is an explanatory diagram of a conventional example.
【図２】 従来のヒステリシスバルブの使用例の説明図FIG. 2 is an explanatory diagram of a usage example of a conventional hysteresis valve.
【図３】 ヒステリシスバルブのない場合の図２のブレ
ーキ状態の説明図FIG. 3 is an explanatory diagram of a braking state of FIG. 2 in the case where there is no hysteresis valve.
【図４】 ヒステリシスバルブを設けた場合の図２のブ
レーキ状態の説明図FIG. 4 is an explanatory diagram of a braking state of FIG. 2 when a hysteresis valve is provided.
【図５】 請求項１の発明の実施例の線図FIG. 5 is a diagram of an embodiment of the invention of claim 1;
【図６】 図５の制御状態の線図FIG. 6 is a diagram of the control state of FIG.
【図７】 請求項２の発明の実施例の線図FIG. 7 is a diagram of an embodiment of the invention of claim 2;
【図８】 図７の制御状態の線図8 is a diagram of the control state of FIG.
１ ケーシング ２ 導入口 ３
導出口 ４ タンク口 ５ ばね ６
ピストン ６ａ ヘッド側室 ６ｂ ロッド側室 ７
スプール弁 ７ａ 第１位置 ７ｂ 第２位置 ８
シーケンス弁 ９ａ 第１位置 ９ｂ 第２位置1 Casing 2 Inlet 3
Outlet port 4 Tank port 5 Spring 6
Piston 6a Head side chamber 6b Rod side chamber 7
Spool valve 7a 1st position 7b 2nd position 8
Sequence valve 9a 1st position 9b 2nd position
Claims (4)
と制御パイロット流体の導出口及びタンク口を備えたケ
ーシング内に、一端にばねによる押圧力が作用し他端に
片ロッド形のピストンの押圧力が作用したスプール弁を
設け、該スプール弁は、該ばねの押圧力が該ピストンの
押圧力よりも優勢のときに、該導入口、導出口、該ピス
トンのロッド側室及びヘッド側室を相互に接続する第１
位置と、該ピストンの押圧力が該ばねの押圧力よりも優
勢のときに、該ロッド側室とタンク口を接続すると共に
該導入口と該導出口をシーケンス弁及び該スプール弁を
介して接続し、且つ該ヘッド側室を該導入口に接続する
第２位置の切換位置を有することを特徴とするヒステリ
シスバルブ装置。1. A casing provided with a pilot fluid inlet, a control pilot fluid outlet, and a tank inlet, the pressure of which changes, is pressed by a spring at one end and a single rod piston is pushed at the other end. A spool valve under pressure is provided, and the spool valve mutually connects the inlet port, the outlet port, the rod side chamber and the head side chamber of the piston when the pressing force of the spring is superior to the pressing force of the piston. First to connect
Position and when the pressing force of the piston is superior to the pressing force of the spring, the rod side chamber is connected to the tank port, and the inlet port and the outlet port are connected via the sequence valve and the spool valve. And a hysteresis valve device having a switching position of a second position for connecting the head side chamber to the introduction port.
と制御パイロット流体の導出口及びタンク口を備えたケ
ーシング内に、一端にばねによる押圧力が作用し他端に
片ロッド形のピストンの押圧力が作用したスプール弁を
設け、該スプール弁は、該ばねの押圧力が該ピストンの
押圧力よりも優勢のときに、該導入口をシーケンス弁を
介して導出口、該ピストンのロッド側室及びヘッド側室
に接続する第１位置と、該ピストンの押圧力が該ばねの
押圧力よりも優勢のときに、該ロッド側室とタンク口を
接続すると共に該導出口と該導入口及び該ヘッド側室を
相互に接続する第２位置の切換位置を有することを特徴
とするヒステリシスバルブ装置。2. A casing having a pilot fluid inlet, a control pilot fluid outlet, and a tank inlet, the pressure of which changes, is pressed by a spring at one end and a single rod piston is pushed at the other end. A spool valve acted on by pressure is provided, and when the pressing force of the spring is superior to the pressing force of the piston, the spool valve is configured so that the inlet port is an outlet port via a sequence valve, the rod side chamber of the piston, and When the pressing force of the piston is superior to the pressing force of the spring and the first position connected to the head side chamber, the rod side chamber is connected to the tank port, and the outlet port, the introduction port and the head side chamber are connected to each other. A hysteresis valve device, characterized in that it has a switching position of a second position connected to each other.
自在であることを特徴とする請求項１又は２に記載のヒ
ステリシスバルブ装置。3. The hysteresis valve device according to claim 1, wherein the sequence valve has a variable pressure drop characteristic.
徴とする請求項１又は２に記載のヒステリシスバルブ装
置。4. The hysteresis valve device according to claim 1, wherein the spring has a variable spring force.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22496794A JP3532257B2 (en) | 1994-09-20 | 1994-09-20 | Hysteresis valve device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22496794A JP3532257B2 (en) | 1994-09-20 | 1994-09-20 | Hysteresis valve device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0893961A true JPH0893961A (en) | 1996-04-12 |
| JP3532257B2 JP3532257B2 (en) | 2004-05-31 |
Family
ID=16822019
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22496794A Expired - Lifetime JP3532257B2 (en) | 1994-09-20 | 1994-09-20 | Hysteresis valve device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3532257B2 (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61204054U (en) * | 1985-06-13 | 1986-12-22 | ||
| JPS61204004U (en) * | 1985-06-13 | 1986-12-22 | ||
| JPH03381U (en) * | 1989-05-26 | 1991-01-07 | ||
| JPH03140683A (en) * | 1989-10-24 | 1991-06-14 | Komatsu Ltd | spool valve |
-
1994
- 1994-09-20 JP JP22496794A patent/JP3532257B2/en not_active Expired - Lifetime
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61204054U (en) * | 1985-06-13 | 1986-12-22 | ||
| JPS61204004U (en) * | 1985-06-13 | 1986-12-22 | ||
| JPH03381U (en) * | 1989-05-26 | 1991-01-07 | ||
| JPH03140683A (en) * | 1989-10-24 | 1991-06-14 | Komatsu Ltd | spool valve |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3532257B2 (en) | 2004-05-31 |
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