JP2002168205A - Pressure reducing valve - Google Patents
Pressure reducing valveInfo
- Publication number
- JP2002168205A JP2002168205A JP2000367766A JP2000367766A JP2002168205A JP 2002168205 A JP2002168205 A JP 2002168205A JP 2000367766 A JP2000367766 A JP 2000367766A JP 2000367766 A JP2000367766 A JP 2000367766A JP 2002168205 A JP2002168205 A JP 2002168205A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- piston
- secondary pressure
- spool
- reducing 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.)
- Granted
Links
Landscapes
- Servomotors (AREA)
- Safety Valves (AREA)
- Mechanically-Actuated Valves (AREA)
- Control Of Fluid Pressure (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は通称パイロットバル
ブ、正確には押力を受けてこの押力に応じた二次圧力を
減圧出力する減圧弁に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pilot valve, and more particularly, to a pressure reducing valve which receives a pressing force and outputs a reduced secondary pressure corresponding to the pressing force.
【０００２】[0002]
【従来の技術】従来知られた減圧弁の例を図４に示す。
これを第１従来形態とする。弁本体１４０は一次圧力ポ
ート４９、二次圧力ポート２８及びドレンポート２６を
備えたブロック１４１を有しており、一次圧力ポート４
９は油圧ポンプ等の油圧源２３に接続し、ドレンポート
２６はタンク２４に接続している。2. Description of the Related Art FIG. 4 shows an example of a conventionally known pressure reducing valve.
This is referred to as a first conventional mode. The valve body 140 has a block 141 having a primary pressure port 49, a secondary pressure port 28, and a drain port 26.
9 is connected to a hydraulic source 23 such as a hydraulic pump, and the drain port 26 is connected to a tank 24.
【０００３】弁本体１４０は一次圧力ポート４９、二次
圧力ポート２８及びドレンポート２６の間を連通自在と
するスプール５１を備えると共に、スプール５１に動き
を与えるピストン１５２を備える。ピストン１５２は自
らの他端側に当接する第１ばね５３によって一端側へ押
し上げられ、揺動自在なレバー４４に固設したリンク５
７に一端側で当接している。スプール５１は他端側へ向
けてピストン１５２に垂下され、ピストン１５２の他端
側に当接する第２ばね５４によって他端側方向に付勢さ
れる。[0003] The valve body 140 has a spool 51 that allows free communication between the primary pressure port 49, the secondary pressure port 28 and the drain port 26, and a piston 152 that moves the spool 51. The piston 152 is pushed up to one end by a first spring 53 abutting on its other end, and is fixed to a swingable lever 44.
7 at one end. The spool 51 is suspended from the piston 152 toward the other end, and is urged in the other end direction by the second spring 54 abutting on the other end of the piston 152.
【０００４】レバー４４を中立位置から矢印ａ方向に操
作して作動位置とするとリンク５７によりピストン１５
２が他端側方向に押し下げられ、スプール５１が第２ば
ね５４を介して押し下げられて圧油供給状態となる。す
なわちこの位置では二次圧力ポート２８と一次圧力ポー
ト４９との間は連通状態、二次圧力ポート２８とドレン
ポート２６との間は遮断状態となり、二次圧力ポート２
８の圧力が上昇してここより圧油が供給される。このと
き、二次圧力ポート２８の圧力が第２ばね５４に抗して
スプール５１を一端側方向へ押し上げようとする。スプ
ール５１を押し上げると二次圧力ポート２８の圧力は下
がる。これにより、スプール５１は、二次圧力ポート２
８の圧力による推力と第２ばね５４の推力とがつりあう
位置に収束し、もって二次圧力ポート２８の圧力すなわ
ち二次圧力は、第２ばね５４の縮み量すなわちレバー４
４の操作量に応じた圧力となり、すなわちこれが二次圧
力となる。When the lever 44 is moved from the neutral position in the direction of arrow a to the operating position, the link 57
2 is pushed down toward the other end, and the spool 51 is pushed down via the second spring 54 to be in a pressure oil supply state. That is, at this position, a communication state is established between the secondary pressure port 28 and the primary pressure port 49, and a cutoff state is established between the secondary pressure port 28 and the drain port 26.
The pressure of 8 rises and pressure oil is supplied from here. At this time, the pressure of the secondary pressure port 28 tries to push up the spool 51 toward one end side against the second spring 54. When the spool 51 is pushed up, the pressure at the secondary pressure port 28 decreases. Thereby, the spool 51 is connected to the secondary pressure port 2
8 converges to a position where the thrust by the pressure of the second spring 54 and the thrust of the second spring 54 are balanced, so that the pressure at the secondary pressure port 28, that is, the secondary pressure is reduced by the contraction amount of the second spring 54,
The pressure corresponds to the manipulated variable of No. 4, that is, this is the secondary pressure.
【０００５】[0005]
【発明が解決しようとする課題】上記構造の減圧弁で
は、二次圧力でスプール５１に一端側方向の推力が発生
し、これが第２ばね５４を介し、ピストン１５２を押し
上げ、レバー４４に反力として伝わる。したがって二次
圧力の上昇に連れてレバー４４の操作力が増大する。上
記推力はスプール５１の受圧面積に比例するため、大流
量化のためにスプール５１を大型化する場合には、操作
力が過度に大きくなり、操作に支障をきたす。In the pressure reducing valve having the above structure, the secondary pressure generates a thrust in one end of the spool 51, which pushes up the piston 152 via the second spring 54, and the reaction force is applied to the lever 44. It is transmitted as. Therefore, the operating force of the lever 44 increases as the secondary pressure increases. Since the thrust is proportional to the pressure receiving area of the spool 51, when the spool 51 is enlarged to increase the flow rate, the operation force becomes excessively large, which hinders the operation.
【０００６】上記推力による操作力の増大をさけるため
の技術として、例えば特公平０３−５０１２６に記載さ
れた技術がある。これを第２従来形態とする。これは図
５に示すように、スプール１５１（第１従来形態のスプ
ール５１相当）に相対摺動可能に嵌着され、スプール１
５１に発生する一端側方向の推力に見合った他端側方向
の推力を上面に作用させることにより発生させる第２ピ
ストン５８が下端に固着されたロッド５９を、第１ピス
トン１５２（第１従来形態のピストン５２相当）の下端
に垂下状態で保持せしめたものである。第２ピストン５
８に発生する他端側方向の推力が第１ピストン１５２に
作用するため、第２ばね５４を介して伝わる一端側方向
の推力が相殺され、もって二次圧力の上昇に連れてレバ
ー４４の操作力が増大することはなくなる。As a technique for preventing an increase in the operating force due to the thrust, there is a technique described in Japanese Patent Publication No. 03-50126, for example. This is referred to as a second conventional mode. As shown in FIG. 5, this is fitted to a spool 151 (corresponding to the spool 51 of the first conventional embodiment) so as to be relatively slidable.
A rod 59 having a second piston 58 fixed to the lower end generated by applying a thrust in the other end direction corresponding to the thrust in the one end side generated on the upper surface to the upper surface is attached to the first piston 152 (first conventional embodiment). (Corresponding to the piston 52) in a hanging state. Second piston 5
8, the thrust in the other end side acting on the first piston 152 acts on the first piston 152, so that the thrust in the one end side transmitted via the second spring 54 is canceled out, so that the operation of the lever 44 is operated as the secondary pressure increases. The power will not increase.
【０００７】しかしこの減圧弁は、スプール１５１の制
御流量を大きくできない。なぜなら、スプール１５１を
軸方向にロッド５９が貫通しているため、一次圧力ポー
ト４９、二次圧力ポート２８及びドレンポート２６の間
を軸方向に流れる通路面積が（ロッド５９の断面積相当
分）絞られるからである。However, this pressure reducing valve cannot increase the control flow rate of the spool 151. Because the rod 59 penetrates through the spool 151 in the axial direction, the passage area flowing in the axial direction between the primary pressure port 49, the secondary pressure port 28, and the drain port 26 is equivalent to the sectional area of the rod 59. Because it is squeezed.
【０００８】本発明は上記従来の問題点に着目したもの
である。すなわち、二次圧力によって発生する一方向の
推力が操作力を増大させて操作に支障をきたすことのな
いよう、二次圧力に見合った他方向の推力を発生させ
て、両方向の推力を略相殺させる構成を有しながら、上
記構成を持たない従来の減圧弁に比して制御流量の低下
を生じない減圧弁を提供することを目的とする。The present invention focuses on the above conventional problems. In other words, a thrust in the other direction is generated in accordance with the secondary pressure, so that the thrust in one direction generated by the secondary pressure does not increase the operating force and hinder the operation. An object of the present invention is to provide a pressure reducing valve which does not cause a decrease in the control flow rate as compared with a conventional pressure reducing valve which does not have the above configuration, while having a configuration for causing the above.
【０００９】[0009]
【課題を解決するための手段および作用効果】上記目的
を達成するために本発明は、二次圧力を受けると共に対
抗する方向に外部からピストンを介して押力を受け、こ
れによりブロック内に設けた孔内を移動するスプールを
有し、スプールの移動量に応じた二次圧力が一次圧力か
ら減圧生成され、出力自在とされた減圧弁において、前
記一方の二次圧力は、スプールと、ピストンとで受け、
かつ二次圧力の側からピストンへと連通するようにブロ
ック内に設けた油路を経て受けたことを特徴とする。In order to attain the above object, the present invention receives a secondary pressure and receives a pressing force from the outside via a piston in a direction opposite to the secondary pressure, thereby providing the block in the block. A secondary pressure corresponding to the amount of movement of the spool is reduced from the primary pressure, and the one secondary pressure is controlled by a spool and a piston. And received
In addition, it is received via an oil passage provided in the block so as to communicate with the piston from the side of the secondary pressure.
【００１０】また、前記一方の二次圧力は、スプール
と、ピストンに設けた受圧部とで受け、かつ二次圧力の
側からピストンへと連通するようにブロック内に設けた
油路を経て受けると共に、ピストンを内嵌するスリーブ
をブロック内に着脱自在に設け、かつ油路をピストンと
スリーブとの間に接続したことを特徴とする。The one secondary pressure is received by the spool and a pressure receiving portion provided on the piston, and is received via an oil passage provided in the block so as to communicate from the secondary pressure side to the piston. In addition, a sleeve in which the piston is fitted is provided detachably in the block, and an oil passage is connected between the piston and the sleeve.
【００１１】上記構成によれば、ピストンに二次圧力が
作用して一方向の推力が発生するので、スプールに二次
圧力が作用して発生する他方向の推力は減殺され、スプ
ールを移動させる押力が低減して操作性が向上する。し
かも、制御流量の低下などを招くこともない。According to the above construction, since the secondary pressure acts on the piston to generate a thrust in one direction, the thrust generated in the other direction due to the secondary pressure acting on the spool is reduced and the spool is moved. The pressing force is reduced, and the operability is improved. In addition, the control flow rate does not decrease.
【００１２】また、上記のようにピストンと着脱自在な
スリーブとの間に油路を接続するように構成すれば、ピ
ストンとスリーブとの交換により、二次圧力を受ける面
積を変えられ、他方向の推力を減殺する割合を自在に選
定できる。すなわち、機器としての汎用性が向上する。Further, if the oil passage is connected between the piston and the detachable sleeve as described above, the area receiving the secondary pressure can be changed by exchanging the piston and the sleeve, and the other direction can be changed. The rate at which the thrust is reduced can be freely selected. That is, versatility as a device is improved.
【００１３】[0013]
【発明の実施の形態】以下、本発明の実施形態につい
て、図を参照して詳細に説明する。なお、従来形態と図
示形状の異なるものであっても、構成上差異のない要素
については同一の符号を付す。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In addition, the same reference numerals are given to elements having no difference in configuration even if they are different from the conventional embodiment in the illustrated shape.
【００１４】まず、第１実施形態による減圧弁の図を図
１に示す。弁本体４０は一次圧力ポート４９、二次圧力
ポート２８及びドレンポート２６を備えたブロック４１
を有しており、一次圧力ポート４９は油圧ポンプ等の油
圧源２３に接続し、ドレンポート２６はタンク２４に接
続している。弁本体４０の一端側にはレバー４４が揺動
自在に取り付けてある。First, a diagram of a pressure reducing valve according to a first embodiment is shown in FIG. The valve body 40 includes a block 41 having a primary pressure port 49, a secondary pressure port 28, and a drain port 26.
The primary pressure port 49 is connected to a hydraulic source 23 such as a hydraulic pump, and the drain port 26 is connected to the tank 24. A lever 44 is swingably attached to one end of the valve body 40.
【００１５】弁本体４０は、ブロック４１内に、一次圧
力ポート４９、二次圧力ポート２８及びドレンポート２
６の間を連通・遮断するスプール５１を備えると共に、
スプール５１に一端側方向と他端側方向とへの動きを与
えるように摺動自在に挿入したピストン５２を備える。
ピストン５２は自らの他端側に備えたばね受け１２に支
持された第１ばね５３によって一端側に押し上げられて
いる。もってピストン５２は、レバー４４に固設したリ
ンク５７に、自らの一端側に備えた当接部１１で当接し
ている。スプール５１は他端側へ向けてばね受け１２に
垂下され、ばね受け１２に支持された第２ばね５４によ
って他端側方向に付勢される。The valve body 40 includes a primary pressure port 49, a secondary pressure port 28, and a drain port 2 in a block 41.
6 and a spool 51 for communicating and blocking between
It has a piston 52 slidably inserted so as to give movement to the spool 51 in one end direction and the other end direction.
The piston 52 is pushed up to one end by a first spring 53 supported by a spring receiver 12 provided at the other end of the piston 52. Thus, the piston 52 is in contact with the link 57 fixed to the lever 44 by the contact portion 11 provided on one end side of the piston 52. The spool 51 is suspended from the spring receiver 12 toward the other end, and is urged toward the other end by the second spring 54 supported by the spring receiver 12.
【００１６】ここでばね受け１２の径は当接部１１の径
よりも大であり、ばね受け１２と当接部１１との間には
段差部１３が形成される。ブロック４１は、段差部１３
に油圧をかけて他端側方向の推力を発生させる受圧室１
４と、受圧室１４に二次圧力ポート２８の圧力を導入す
る油路１５とを有する。Here, the diameter of the spring receiver 12 is larger than the diameter of the contact part 11, and a step 13 is formed between the spring receiver 12 and the contact part 11. The block 41 includes the step 13
Receiving chamber 1 that generates thrust in the other end direction by applying hydraulic pressure to
4 and an oil passage 15 for introducing the pressure of the secondary pressure port 28 into the pressure receiving chamber 14.
【００１７】次に作動を説明する。レバー４４が中立位
置のときには二次圧力ポート２８が圧油を供給しない状
態である。すなわちスプール５１は第２ばね５４で押し
下げ保持された位置にあり、この位置では二次圧力ポー
ト２８と一次圧力ポート４９との間は遮断状態、二次圧
力ポート２８とドレンポート２６との間は連通状態とな
る。Next, the operation will be described. When the lever 44 is in the neutral position, the secondary pressure port 28 is in a state of not supplying pressure oil. That is, the spool 51 is in a position where it is pushed down and held by the second spring 54, and in this position, the state between the secondary pressure port 28 and the primary pressure port 49 is shut off, and the state between the secondary pressure port 28 and the drain port 26 is The communication state is established.
【００１８】レバー４４を中立位置から矢印ａ方向に操
作して作動位置とすると、リンク５７によりピストン５
２が押し下げられてスプール５１が第２ばね５４を介し
て押し下げられて圧油供給状態となる。すなわちこの位
置では二次圧力ポート２８と一次圧力ポート４９との間
は連通状態、二次圧力ポート２８とドレンポート２６と
の間は遮断状態となり、二次圧力ポート２８の圧力が上
昇して二次圧力ポート２８より圧油が供給される。この
とき、二次圧力ポート２８の圧力が第２ばね５４に抗し
てスプール５１を押し上げようとする。スプール５１を
押し上げると二次圧力ポート２８の圧力は下がる。これ
により、スプール５１は、二次圧力ポート２８の圧力に
よる推力と第２ばね５４の推力とがつりあう位置に収束
し、もって二次圧力ポート２８の圧力は、第２ばね５４
の縮み量すなわちレバー４４の操作量に応じた圧力とな
り、すなわちこれが二次圧力となる。When the lever 44 is operated from the neutral position in the direction of arrow a to the operating position, the link 57
2 is pushed down, and the spool 51 is pushed down via the second spring 54 to be in a pressure oil supply state. That is, at this position, the communication between the secondary pressure port 28 and the primary pressure port 49 is in a communication state, and the communication between the secondary pressure port 28 and the drain port 26 is in a cutoff state. Pressure oil is supplied from the next pressure port 28. At this time, the pressure of the secondary pressure port 28 tries to push up the spool 51 against the second spring 54. When the spool 51 is pushed up, the pressure in the secondary pressure port 28 decreases. As a result, the spool 51 converges to a position where the thrust by the pressure of the secondary pressure port 28 and the thrust of the second spring 54 balance, so that the pressure of the secondary pressure port 28 is reduced by the second spring 54.
, Ie, a pressure corresponding to the amount of operation of the lever 44, ie, a secondary pressure.
【００１９】このとき、二次圧力でスプール５１に一端
側方向の推力が発生し、これが第２ばね５４を介し、ピ
ストン５２を押し上げる。しかし同時に二次圧力が、油
路１５を介して受圧室１４に導入され、段差部１３に作
用して他端側方向の推力を発生させ、ピストン５２を押
し下げる。したがって、スプール５１に発生する一端側
方向の推力による、レバー操作力の増大分は減殺され
る。At this time, the secondary pressure generates a thrust in one end direction on the spool 51, which pushes up the piston 52 via the second spring 54. However, at the same time, the secondary pressure is introduced into the pressure receiving chamber 14 via the oil passage 15 and acts on the step 13 to generate a thrust in the other end side direction, thereby pushing down the piston 52. Therefore, the increase in lever operating force due to the thrust in the one end direction generated on the spool 51 is reduced.
【００２０】以上述べた通り、第１実施形態によれば、
スプールに発生する一端側方向の推力による、レバー操
作力の増大分は減殺されるので、第１従来形態に比して
操作性が向上する。しかも、第２従来形態のようにスプ
ール内を貫通する部材を設ける必要がないので、第１従
来形態に比して大型化や制御流量の低下などといったデ
メリットを生じることもない。As described above, according to the first embodiment,
Since the increase in the lever operation force due to the thrust in the one end direction generated on the spool is reduced, the operability is improved as compared with the first conventional embodiment. Moreover, since there is no need to provide a member that penetrates the inside of the spool as in the second conventional embodiment, there is no disadvantage such as an increase in size and a decrease in the control flow rate as compared with the first conventional embodiment.
【００２１】次に第２実施形態について説明する。第１
実施形態との相違は、ピストンとの間で受圧室を形成す
るブロックの部分を、ブロックに対して着脱自在なスリ
ーブとしたことである。このスリーブとピストンとを対
で交換することにより、受圧室の他端側方向の受圧面積
を変えることができ、レバー操作力の増大分を減殺する
割合を自在に選定できる。Next, a second embodiment will be described. First
The difference from the embodiment is that the block portion forming the pressure receiving chamber between the piston and the piston is a sleeve that is detachable from the block. By exchanging the sleeve and the piston as a pair, the pressure receiving area in the other end side of the pressure receiving chamber can be changed, and the rate at which the increase in lever operating force is reduced can be freely selected.
【００２２】図２に第２実施形態による減圧弁の図を示
し、図３に図２の拡大詳細図を示す。第１実施形態と同
様の部文意ついては同一の符号を付し、説明を省略す
る。FIG. 2 is a view of a pressure reducing valve according to a second embodiment, and FIG. 3 is an enlarged detailed view of FIG. The same reference numerals as in the first embodiment denote the same parts, and a description thereof will be omitted.
【００２３】弁本体９０はブロック９１内に、スプール
５１を備えると共に、スプール５１に動きを与えるピス
トン９２を備える。ピストン９２は、ブロック９１内に
着脱自在に嵌入したスリーブ８０に摺動自在に挿入され
ている。自らの他端側に備えたばね受け６２に支持され
た第１ばね５３によって押し上げられている。もってピ
ストン９２は、レバー４４に固設したリンク５７に、自
らの一端側に備えた当接部６１で当接している。スプー
ル５１は他端側へ向けてばね受け６２に垂下され、ばね
受け６２に支持された第２ばね５４によって他端側方向
に付勢される。The valve body 90 has a spool 51 in a block 91 and a piston 92 for moving the spool 51. The piston 92 is slidably inserted into a sleeve 80 detachably fitted in the block 91. It is pushed up by a first spring 53 supported by a spring receiver 62 provided on its other end. Accordingly, the piston 92 is in contact with the link 57 fixed to the lever 44 at the contact portion 61 provided at one end of the piston 92. The spool 51 is suspended from the spring receiver 62 toward the other end, and is urged toward the other end by the second spring 54 supported by the spring receiver 62.
【００２４】ここでピストン９２はばね受け６２の外径
側の一端側に小径部９３を有し、他端側に大径部９４を
有する。スリーブ８０は内径側の他端側に大径部８２を
有し、一端側に小径部８１を有する。ピストン９２の小
径部９３とスリーブ８０の小径部８１とは径が略等しく
略密着状態で摺動し、ばね受け６２の大径部９４とスリ
ーブ８０の大径部８２とは径が略等しく略密着状態で摺
動する。The piston 92 has a small-diameter portion 93 at one end on the outer diameter side of the spring receiver 62 and a large-diameter portion 94 at the other end. The sleeve 80 has a large diameter portion 82 on the other end side on the inner diameter side and a small diameter portion 81 on one end side. The small-diameter portion 93 of the piston 92 and the small-diameter portion 81 of the sleeve 80 have substantially the same diameter and slide in substantially close contact with each other, and the large-diameter portion 94 of the spring receiver 62 and the large-diameter portion 82 of the sleeve 80 have substantially the same diameter. Slides in close contact.
【００２５】もってばね受け６２の小径部９１とスリー
ブ８０の大径部８２との間には受圧室６４が形成され
る。受圧室６４は二次圧力を導入する油路６５を有す
る。受圧室６４に導入した二次圧力はばね受け６２の小
径部９３と大径部９４との間に形成される段差部６３に
作用して他端側方向の推力を発生させる。A pressure receiving chamber 64 is formed between the small diameter portion 91 of the spring receiver 62 and the large diameter portion 82 of the sleeve 80. The pressure receiving chamber 64 has an oil passage 65 for introducing a secondary pressure. The secondary pressure introduced into the pressure receiving chamber 64 acts on a step 63 formed between the small diameter portion 93 and the large diameter portion 94 of the spring receiver 62 to generate a thrust in the other end side.
【００２６】レバー４４を中立位置から矢印ａ方向に操
作して作動位置とすると、ピストン９２及びスプール５
１が押し下げられて二次圧力ポートが上昇する。この二
次圧力がスプール５１に作用し、ピストン９２を一端側
方向へ押し上げようとする。しかし同時に二次圧力が、
油路６５を介して受圧室６４に導入され、段差部６３に
作用して他端側方向の推力を発生させ、ピストン９２を
押し下げる。したがって、スプール５１に発生する一端
側方向の推力による、レバー操作力の増大分は減殺さ
れ、操作性が向上する。When the lever 44 is operated from the neutral position in the direction of arrow a to the operating position, the piston 92 and the spool 5
1 is depressed and the secondary pressure port rises. This secondary pressure acts on the spool 51 to push up the piston 92 toward one end. But at the same time the secondary pressure,
It is introduced into the pressure receiving chamber 64 via the oil passage 65 and acts on the step 63 to generate a thrust in the other end direction, thereby pushing down the piston 92. Therefore, an increase in lever operating force due to thrust in the one end direction generated on the spool 51 is reduced, and operability is improved.
【００２７】ここでレバー操作力の減殺分は、段差部６
３の受圧面積に比例する。すなわち、ばね受け６２の小
径部９１の径をｄ１、大径部９４の径をｄ２とすれば、
受圧面積は（ｄ２×ｄ２−ｄ１×ｄ１）×π／４であ
り、レバー操作力の減殺分は（ｄ２×ｄ２−ｄ１×ｄ
１）に比例する。Here, the decrement of the lever operating force is determined by the step portion 6.
3 is proportional to the pressure receiving area. That is, if the diameter of the small diameter portion 91 of the spring receiver 62 is d1 and the diameter of the large diameter portion 94 is d2,
The pressure receiving area is (d2 × d2-d1 × d1) × π / 4, and the decrement of the lever operating force is (d2 × d2-d1 × d
It is proportional to 1).
【００２８】第２実施形態によれば、第１実施形態の効
果に加えて、スリーブ８０とピストン９２とを交換する
ことにより、ｄ１及び／又はｄ２を変えることができ
る。無論ピストン９２をｄ１及び／又はｄ２の値が異な
るものに交換する場合、略密着状態を維持するためにス
リーブ８０もまた、ピストン９２と対で交換する必要が
ある。ピストン９２とスリーブ８０とを対で交換し、ｄ
１及び／又はｄ２を変えると、受圧面積を変えることに
なる。すると、ピストン９２に発生する他端側方向の推
力を変えることになるので、レバー操作力の増大分を減
殺する割合を自在に選定できる。According to the second embodiment, in addition to the effects of the first embodiment, d1 and / or d2 can be changed by exchanging the sleeve 80 and the piston 92. Of course, if the piston 92 is replaced with one having a different value of d1 and / or d2, the sleeve 80 must also be replaced with the piston 92 in order to maintain a substantially close contact. The piston 92 and the sleeve 80 are exchanged in pairs, and d
Changing 1 and / or d2 will change the pressure receiving area. Then, the thrust generated in the other end side of the piston 92 is changed, so that the rate at which the increase in the lever operating force is reduced can be freely selected.
【００２９】一般にレバー操作力の大きさは、操作する
人間の好み、操作頻度、レバー長さ、及びその他諸々の
条件で、最適とされる要求値が異なる。したがって、上
記のようにレバー操作力の増大分を減殺する割合を自在
に選定できる構造とすることで、弁本体に大きく手を加
えることなく、異なる要求値に対応できる。すなわち、
機器としての汎用性が向上する。In general, the required value of the lever operation force differs depending on the preference of the operator, the operation frequency, the lever length, and other various conditions. Therefore, as described above, by adopting a structure capable of freely selecting a ratio for reducing the increase in the lever operation force, it is possible to meet different required values without significantly modifying the valve body. That is,
The versatility as a device is improved.
【００３０】なお、本発明の減圧弁は、必ずしも揺動自
在なレバーによって操作するものでなくともよい。例え
ば直線方向にピストンを押込んで操作するものであって
もよい。The pressure reducing valve of the present invention does not necessarily need to be operated by a swingable lever. For example, the operation may be performed by pushing a piston in a linear direction.
【００３１】以上実施形態を示して説明の通り、本発明
の減圧弁によれば、二次圧力が作用して発生する推力に
よる、操作力の増大分は減殺され、操作性が向上する。
しかも、制御流量の低下などを招くことなくこれを達成
できる。As described above with reference to the embodiment, according to the pressure reducing valve of the present invention, the increase in the operating force due to the thrust generated by the action of the secondary pressure is reduced, and the operability is improved.
Moreover, this can be achieved without lowering the control flow rate.
【図１】本発明の第１実施形態に係る減圧弁の図であ
る。FIG. 1 is a diagram of a pressure reducing valve according to a first embodiment of the present invention.
【図２】本発明の第２実施形態に係る減圧弁の図であ
る。FIG. 2 is a diagram of a pressure reducing valve according to a second embodiment of the present invention.
【図３】図２の詳細図である。FIG. 3 is a detailed view of FIG. 2;
【図４】第１従来形態に係る減圧弁の図である。FIG. 4 is a diagram of a pressure reducing valve according to a first conventional embodiment.
【図５】第２従来形態に係る減圧弁の図である。FIG. 5 is a diagram of a pressure reducing valve according to a second conventional embodiment.
１５，６５…油路、２８…二次圧力ポート、４１，９１
…ブロック、５１…スプール、５２，９２…ピストン、
６３…段差部、８０…スリーブ。15, 65: oil passage, 28: secondary pressure port, 41, 91
... block, 51 ... spool, 52,92 ... piston,
63: stepped portion, 80: sleeve.
───────────────────────────────────────────────────── フロントページの続き (72)発明者 石崎 直樹 栃木県小山市横倉新田400 株式会社小松 製作所小山工場内 Ｆターム(参考） 3H002 BA02 BB06 BC07 BD04 BE01 3H060 AA09 BB01 FF03 FF08 HH04 3H063 AA09 BB08 CC04 DA05 DB11 GG05 GG13 ────────────────────────────────────────────────── ─── Continued on the front page (72) Inventor Naoki Ishizaki 400 Yokokura Nitta, Oyama City, Tochigi Prefecture Komatsu Plant Koyama Plant F-term (reference) 3H002 BA02 BB06 BC07 BD04 BE01 3H060 AA09 BB01 FF03 FF08 HH04 3H063 AA09 BB08 CC04 DA05 DB11 GG05 GG13
Claims (2)
外部からピストンを介して押力を受け、これによりブロ
ック内に設けた孔内を移動するスプールを有し、スプー
ルの移動量に応じた二次圧力が一次圧力から減圧生成さ
れ、出力自在とされた減圧弁において、 前記一方の二次圧力は、スプール(51)と、ピストン(52)
とで受け、かつ二次圧力の側からピストン(52)へと連通
するようにブロック(41)内に設けた油路(15)を経て受け
たことを特徴とする減圧弁。1. A spool which receives a secondary pressure and receives a pressing force from the outside via a piston in a direction opposite to the secondary pressure, thereby moving in a hole provided in the block. In the pressure reducing valve in which the secondary pressure is reduced in pressure from the primary pressure and the output is free, the one secondary pressure includes a spool (51) and a piston (52).
And a pressure reducing valve received through an oil passage (15) provided in the block (41) so as to communicate from the side of the secondary pressure to the piston (52).
外部からピストンを介して押力を受け、これによりブロ
ック内に設けた孔内を移動するスプールを有し、スプー
ルの移動量に応じた二次圧力が一次圧力から減圧生成さ
れ、出力自在とされた減圧弁において、 前記一方の二次圧力は、スプール(51)と、ピストン(92)
に設けた受圧部(63)とで受け、かつ二次圧力の側からピ
ストン(92)へと連通するようにブロック(91)内に設けた
油路(65)を経て受けると共に、 ピストン(92)を内嵌するスリーブ(80)をブロック(91)内
に着脱自在に設け、 かつ油路(65)をピストン(92)とスリーブ(80)との間に接
続したことを特徴とする減圧弁。2. A spool which receives a secondary pressure and receives a pressing force from the outside via a piston in a direction opposite to the secondary pressure, thereby moving in a hole provided in the block. In the pressure reducing valve in which the secondary pressure is reduced in pressure from the primary pressure and the output is free, the one of the secondary pressures includes a spool (51) and a piston (92).
And received through an oil passage (65) provided in a block (91) so as to communicate with the piston (92) from the side of the secondary pressure to the piston (92). A pressure reducing valve characterized in that a sleeve (80) for internally fitting therein is removably provided in the block (91), and an oil passage (65) is connected between the piston (92) and the sleeve (80). .
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000367766A JP4562902B2 (en) | 2000-12-01 | 2000-12-01 | Pressure reducing valve |
| TW90126676A TW542876B (en) | 2000-12-01 | 2001-10-29 | Pressure reducing valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000367766A JP4562902B2 (en) | 2000-12-01 | 2000-12-01 | Pressure reducing valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2002168205A true JP2002168205A (en) | 2002-06-14 |
| JP4562902B2 JP4562902B2 (en) | 2010-10-13 |
Family
ID=18838131
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000367766A Expired - Fee Related JP4562902B2 (en) | 2000-12-01 | 2000-12-01 | Pressure reducing valve |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4562902B2 (en) |
| TW (1) | TW542876B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007002900A (en) * | 2005-06-22 | 2007-01-11 | Komatsu Ltd | Pilot valve |
| JP2007024180A (en) * | 2005-07-15 | 2007-02-01 | Komatsu Ltd | Pilot valve |
| JP2007078085A (en) * | 2005-09-14 | 2007-03-29 | Hitachi Constr Mach Co Ltd | Hydraulic operation device of working machine |
| JP2012508360A (en) * | 2008-11-12 | 2012-04-05 | ボッシュ・レックスロス・デー．エス．アイ． | Especially hydraulic remote control type pressure regulator |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113431907B (en) * | 2020-03-23 | 2023-03-14 | 林庆辉 | Fluid valve integrating opening, closing and pressure reducing functions |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63110703U (en) * | 1987-01-12 | 1988-07-16 | ||
| WO1996015374A1 (en) * | 1994-11-14 | 1996-05-23 | Komatsu Ltd. | Hydraulic pilot valve |
| JPH09177712A (en) * | 1995-12-21 | 1997-07-11 | Hitachi Constr Mach Co Ltd | Pressure reducing valve type pilot valve |
| JP2000136802A (en) * | 1998-11-02 | 2000-05-16 | Hitachi Constr Mach Co Ltd | Pressure reducing valve type pilot valve |
-
2000
- 2000-12-01 JP JP2000367766A patent/JP4562902B2/en not_active Expired - Fee Related
-
2001
- 2001-10-29 TW TW90126676A patent/TW542876B/en not_active IP Right Cessation
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63110703U (en) * | 1987-01-12 | 1988-07-16 | ||
| WO1996015374A1 (en) * | 1994-11-14 | 1996-05-23 | Komatsu Ltd. | Hydraulic pilot valve |
| JPH09177712A (en) * | 1995-12-21 | 1997-07-11 | Hitachi Constr Mach Co Ltd | Pressure reducing valve type pilot valve |
| JP2000136802A (en) * | 1998-11-02 | 2000-05-16 | Hitachi Constr Mach Co Ltd | Pressure reducing valve type pilot valve |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007002900A (en) * | 2005-06-22 | 2007-01-11 | Komatsu Ltd | Pilot valve |
| JP2007024180A (en) * | 2005-07-15 | 2007-02-01 | Komatsu Ltd | Pilot valve |
| JP4689382B2 (en) * | 2005-07-15 | 2011-05-25 | 株式会社小松製作所 | Pilot valve |
| JP2007078085A (en) * | 2005-09-14 | 2007-03-29 | Hitachi Constr Mach Co Ltd | Hydraulic operation device of working machine |
| JP2012508360A (en) * | 2008-11-12 | 2012-04-05 | ボッシュ・レックスロス・デー．エス．アイ． | Especially hydraulic remote control type pressure regulator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4562902B2 (en) | 2010-10-13 |
| TW542876B (en) | 2003-07-21 |
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