JP4989676B2 - Pressure regulating valve - Google Patents

Pressure regulating valve Download PDF

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JP4989676B2
JP4989676B2 JP2009106494A JP2009106494A JP4989676B2 JP 4989676 B2 JP4989676 B2 JP 4989676B2 JP 2009106494 A JP2009106494 A JP 2009106494A JP 2009106494 A JP2009106494 A JP 2009106494A JP 4989676 B2 JP4989676 B2 JP 4989676B2
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transmission
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JP2010255748A (en
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直 八木
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Maruyama Manufacturing Co Inc
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a pressure regulating valve easy in a fine adjustment of pressure, using a spring of proper strength, by switching to a low pressure state and a high pressure state with springs for high pressure and low pressure. <P>SOLUTION: This pressure regulating valve includes disc spring 28 and a compression coil spring 29 arranged inside the disc spring 28. A cylindrical first collar 35 for transmitting a load is arranged between a valve 27 and the disc spring 28. A second collar 36 for transmitting the load is arranged between the valve 27 and the compression coil spring 29 on the inside of the first collar 35. The first collar 35 is connected with a handle 52 to be put in any of a transmission state capable of moving this first collar 35 to the valve side and capable of transmitting a load of the disc spring 28 to the valve 27 and a non-transmission state of regulating the movement to the valve 27 side of the first collar 35 and making the load of the disc spring unable to be transmitted to the valve 27. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

本発明は、ポンプの吐出圧の調節等に用いられる調圧弁に関する。   The present invention relates to a pressure regulating valve used for adjusting a discharge pressure of a pump.

従来、圧縮ばねで弁を弁座に付勢した状態で、圧縮ばねの圧縮度合いを例えばねじ部材のねじ込み量で調整することにより、調圧可能な調圧弁が知られている（例えば、特許文献１参照）。このような調圧弁の用途の１つとしては、薬剤散布用のポンプの吐出圧を調圧することが挙げられる。   Conventionally, there is known a pressure regulating valve capable of regulating pressure by adjusting the degree of compression of the compression spring by, for example, the screwing amount of a screw member in a state where the valve is urged to the valve seat by the compression spring (for example, Patent Documents). 1). One application of such a pressure regulating valve is to regulate the discharge pressure of a pump for spraying medicine.

このような調圧弁には、低圧散布と高圧散布とを切り替え可能なものがある。
図１０に、低圧散布と高圧散布とに切り替え可能な調圧弁の例を示す。
この調圧弁は、ボディ１を備え、ボディ１にはポンプの吐出口に連通する流入口１１と、余液口１２が設けられている。流入口１１には、弁座３とこの弁座３に接離可能な弁２とが設けられている。弁２の上側には、ばね受４等の後述のばねの荷重を伝達する伝達部材が上下動自在に配置され、当該ばね受４の上に、有蓋円筒状のばね筒５に収納された皿ばね６と圧縮コイルばね７が配置されている。 Some such pressure regulating valves can switch between low-pressure spraying and high-pressure spraying.
FIG. 10 shows an example of a pressure regulating valve that can be switched between low-pressure spraying and high-pressure spraying.
This pressure regulating valve includes a body 1, and the body 1 is provided with an inflow port 11 communicating with a discharge port of a pump and a surplus liquid port 12. The inflow port 11 is provided with a valve seat 3 and a valve 2 that can contact and separate from the valve seat 3. On the upper side of the valve 2, a transmission member for transmitting a load of a spring, such as a spring receiver 4, which will be described later, is arranged so as to be movable up and down, and on the spring receiver 4 is a dish housed in a covered cylindrical spring cylinder 5. A spring 6 and a compression coil spring 7 are arranged.

皿ばね６は、複数個が交互に表裏を反対にして上下に積層されている。これらの皿ばね６の内側に圧縮コイルばね７が配置されている。圧縮コイルばね７は、低圧散布用に用いられ、低荷重のばねとなっており、皿ばね６は、高圧散布用に用いられ、高荷重のばねとなっている。圧縮コイルばね７の圧縮されていない状態での長さ（自由高さ）は、皿ばね６の長さ（自由高さ）より長くなっている。   A plurality of disc springs 6 are stacked one above the other with the front and back alternately. A compression coil spring 7 is disposed inside these disc springs 6. The compression coil spring 7 is used for low-pressure spraying and is a low-load spring, and the disc spring 6 is used for high-pressure spraying and is a high-load spring. The length (free height) of the compression coil spring 7 in an uncompressed state is longer than the length (free height) of the disc spring 6.

ばね筒５の上端部中央には、握り８が螺合されており、握り８をねじ込むことにより、ばね押部材９を介して圧縮コイルばね７および皿ばね６を圧縮できるようになっている。
ばね受４とばね押部材９との間に配置された圧縮コイルばね７および皿ばね６において、圧縮コイルばね７の方が自由高さが長いので、握り８をねじ込んだ際に、締め付けが緩い状態では、圧縮コイルばね７だけが圧縮され、皿ばね６は圧縮されず、圧縮コイルばね７の付勢力だけが弁２に作用することになり、これにより調圧弁は、低荷重の状態となるので、ポンプの吐出圧が低圧状態となって、低圧散布を行う状態となる。 A grip 8 is screwed into the center of the upper end of the spring cylinder 5, and the compression coil spring 7 and the disc spring 6 can be compressed via the spring pressing member 9 by screwing the grip 8.
In the compression coil spring 7 and the disc spring 6 disposed between the spring receiver 4 and the spring pressing member 9, the compression coil spring 7 has a longer free height, so that when the grip 8 is screwed in, the tightening is loose. In the state, only the compression coil spring 7 is compressed, the disc spring 6 is not compressed, and only the urging force of the compression coil spring 7 acts on the valve 2, thereby the pressure regulating valve is in a low load state. Therefore, the discharge pressure of the pump becomes a low pressure state, and the low pressure spraying is performed.

握り８をねじ込んでさらに締め付けていくと、圧縮コイルばね７だけではなく皿ばね６も圧縮されることになり、弁２には圧縮コイルばね７と皿ばね６の付勢力が作用することになり、これにより調圧弁は、高荷重の状態となるので、ポンプの吐出圧が高圧状態となって、高圧散布を行う状態となる。   When the grip 8 is screwed and further tightened, not only the compression coil spring 7 but also the disc spring 6 is compressed, and the urging force of the compression coil spring 7 and the disc spring 6 acts on the valve 2. Thus, since the pressure regulating valve is in a high load state, the discharge pressure of the pump is in a high pressure state, and the high pressure spraying is performed.

特開２００３−４１５６号公報JP 2003-4156 A

ところで、このような低圧散布と高圧散布とが可能な調圧弁においては、高圧で使用する場合に、高圧用の皿ばね６だけではなく、低圧用の圧縮コイルばね７も圧縮される。すなわち、圧縮コイルばね７と皿ばね６とを圧縮する際に、低圧散布用の圧縮コイルばね７が先に圧縮され、皿ばね６が圧縮される前の段階までにおいて、低圧散布のための荷重を弁２に付与することになる。したがって、圧縮コイルばね７は、皿ばね６が圧縮される前の段階までの低圧散布のための仕様値を備えていればよいことになる。   By the way, in such a pressure regulating valve capable of low pressure spraying and high pressure spraying, not only the high pressure disc spring 6 but also the low pressure compression coil spring 7 is compressed when used at a high pressure. That is, when the compression coil spring 7 and the disc spring 6 are compressed, the load for the low-pressure application is compressed before the compression coil spring 7 for low-pressure application is compressed first and the disc spring 6 is compressed. Is given to the valve 2. Therefore, the compression coil spring 7 only needs to have a specification value for low-pressure spraying up to the stage before the disc spring 6 is compressed.

しかし、さらに握りを回転させてねじ込むと、皿ばね６が圧縮され、高圧散布のための荷重を弁２に付与することになるが、この際に、圧縮コイルばね７がさらに上述の仕様値の対応範囲以上に圧縮されることになるので、許容応力値の関係で、実際の圧縮コイルばね７の仕様値は、上述の低圧散布に必要とされる仕様値より高圧用の仕様値とする必要がある。
このため圧縮コイルばね７を大きくする必要が生じる。この際に圧縮コイルばね７が皿ばね６の中央の穴内に収容された状態なので、圧縮コイルばね７が大きくなった場合に、皿ばね６も大きくする必要が生じ、これによりばね筒５も大きくなってしまう。 However, when the grip is further rotated and screwed in, the disc spring 6 is compressed, and a load for high-pressure spraying is applied to the valve 2. At this time, the compression coil spring 7 further has the above-mentioned specification value. Since it is compressed beyond the corresponding range, the actual specification value of the compression coil spring 7 is required to be higher than the specification value required for the above-mentioned low-pressure spraying because of the allowable stress value. There is.
For this reason, the compression coil spring 7 needs to be enlarged. At this time, since the compression coil spring 7 is accommodated in the central hole of the disc spring 6, when the compression coil spring 7 becomes large, the disc spring 6 needs to be enlarged. turn into.

また、皿ばね６も大きくなることで、高圧散布に必要な仕様値よりさらに高圧用の設定の仕様値となってしまう虞がある。
このように圧縮コイルばね７や皿ばね６が必要以上に大きくなると、ばね定数も大きくなってしまい、低圧散布および高圧散布とも調圧性能がよくない調圧弁となってしまう。すなわち、圧縮コイルばね７および皿ばね６が必要以上にばね定数が大きくなることにより、握り８のねじ込み量を少し増やしただけで荷重が大きく変わり、細かな調圧がし難い調圧弁となってしまう。
また、上述のように圧縮コイルばねは、皿ばね６が圧縮される際にもさらに圧縮されることで、圧縮量が大きくなり強度上不利となる。 Further, since the disc spring 6 is also increased, there is a possibility that the specification value for the high pressure setting may be further increased than the specification value necessary for high-pressure spraying.
When the compression coil spring 7 and the disc spring 6 become larger than necessary in this way, the spring constant also increases, resulting in a pressure regulating valve with poor pressure regulation performance for both low pressure spraying and high pressure spraying. That is, since the spring constant of the compression coil spring 7 and the disc spring 6 becomes larger than necessary, the load changes greatly only by slightly increasing the screwing amount of the grip 8, and the pressure regulating valve is difficult to finely regulate. End up.
Further, as described above, the compression coil spring is further compressed even when the disc spring 6 is compressed, so that the amount of compression becomes large and disadvantageous in terms of strength.

本発明は、前記事情に鑑みて為されたもので、高圧用圧縮ばねと、低圧用圧縮ばねとを用いて、高圧での使用と低圧での使用を可能とする際に、低圧用圧縮ばねが必要以上に大きく圧縮されるのを防止し、各圧での使用に適した仕様値の圧縮ばねを使用可能とすることにより、圧力の微調整を容易とする調圧弁を提供することを目的とする。   The present invention has been made in view of the above circumstances, and uses a high pressure compression spring and a low pressure compression spring to enable use at a high pressure and a low pressure. The purpose of the present invention is to provide a pressure regulating valve that facilitates fine adjustment of pressure by preventing compression of pressure more than necessary and enabling the use of a compression spring with a specification value suitable for use at each pressure. And

前記目的を達成するために、請求項１に記載の調圧弁は、圧縮量調整手段（４０）により圧縮量を調整可能な圧縮ばね（２８，２９）の荷重を弁（２７）に作用させつつ当該弁（２７）と弁座（２６）との間に液体を通過させて圧力を生じさせる調圧弁において、
前記圧縮ばね（２８，２９）として、第１のばね（２８）と、当該第１のばね（２８）より低い圧力を生じさせる第２のばね（２９）とを備え、
前記弁（２７）と前記第１のばね（２８）との間に前記弁（２７）に前記第１のばね（２８）の荷重を伝達させる第１の伝達部材（３５）が設けられ、前記弁（２７）と前記第２のばね（２９）との間に前記弁（２７）に前記第２のばね（２９）の荷重を伝達させる第２の伝達部材（３６）が設けられ、
前記第１の伝達部材（３５）には、当該第１の伝達部材（３５）を前記弁（２７）側に移動可能として前記第１のばね（２８）の荷重を前記弁（２７）に伝達可能とする伝達状態と、当該第１の伝達部材（３５）の弁（２７）側への移動を規制して前記第１のばね（２８）の荷重を前記弁（２７）に伝達不可とする非伝達状態とのいずれかとする切り替え手段（５０）が設けられていることを特徴とする。 In order to achieve the object, the pressure regulating valve according to claim 1 is configured to apply a load of a compression spring (28, 29) whose compression amount can be adjusted by the compression amount adjusting means (40) to the valve (27). In a pressure regulating valve that generates a pressure by passing a liquid between the valve (27) and the valve seat (26),
The compression springs (28, 29) include a first spring (28) and a second spring (29) that generates a lower pressure than the first spring (28),
A first transmission member (35) for transmitting the load of the first spring (28) to the valve (27) is provided between the valve (27) and the first spring (28), and A second transmission member (36) for transmitting the load of the second spring (29) to the valve (27) is provided between the valve (27) and the second spring (29),
In the first transmission member (35), the load of the first spring (28) is transmitted to the valve (27) by allowing the first transmission member (35) to move toward the valve (27). The transmission state to be enabled and the movement of the first transmission member (35) to the valve (27) side are restricted so that the load of the first spring (28) cannot be transmitted to the valve (27). Switching means (50) for switching between the non-transmission state and the non-transmission state is provided.

請求項２に記載の調圧弁は、請求項１に記載の発明において、前記第１のばね（２８）および前記第２のばね（２９）と、前記第１の伝達部材（３５）および第２の伝達部材（３６）とを軸方向に並べた状態で収容する筒状のばね筒（２５）を備え、
前記第１のばね（２８）と、前記第２のばね（２９）とが内外に重なるように同軸上に配置され、
第１の伝達部材（３５）と第２の伝達部材（３６）とが内外に重なるように同軸上に配置され、
前記切り換え手段は、前記ばね筒（２５）と前記第１の伝達部材と前記第２の伝達部材とを貫通するとともに、前記伝達状態の際に前記弁（２７）側への移動が許容され、前記非伝達状態の際に前記弁側の移動が規制されるピン（５１）を備え、
前記ばね筒（２５）および第２の伝達部材（３６）には、前記ピン（５１）が貫通するとともに前記ピン（５１）の前記弁（２７）側への移動を許容する長穴（２５ｃ、３６ａ）が形成され、
第１の伝達部材（３５）には、当該第１の伝達部材が前記ピンと一体に移動するように前記ピンが貫通した状態で嵌合する貫通孔（３５ａ）が形成されていることを特徴とする。 A pressure regulating valve according to a second aspect is the pressure regulating valve according to the first aspect, wherein the first spring (28) and the second spring (29), the first transmission member (35) and the second A cylindrical spring cylinder (25) that accommodates the transmission member (36) in an axially arranged state,
The first spring (28) and the second spring (29) are arranged coaxially so as to overlap inside and outside,
The first transmission member (35) and the second transmission member (36) are arranged coaxially so as to overlap inside and outside,
The switching means penetrates the spring cylinder (25), the first transmission member and the second transmission member, and is allowed to move toward the valve (27) in the transmission state. A pin (51) that restricts movement of the valve side in the non-transmission state;
In the spring cylinder (25) and the second transmission member (36), the pin (51) penetrates and a long hole (25c, which allows the pin (51) to move to the valve (27) side). 36a) is formed,
The first transmission member (35) is formed with a through hole (35a) that fits in a state where the pin penetrates so that the first transmission member moves integrally with the pin. To do.

請求項３に記載の調圧弁は、請求項２に記載の発明において、前記切り替え手段（５０）は、前記伝達状態と前記非伝達状態とを切り替えるハンドル（５２）を備え、
前記ハンドル（５２）には、前記ばね筒（２５）を貫通した前記ピン（５１）の端部に係合して当該ピンを回転中心とし前記伝達状態となる角度と前記非伝達状態となる角度との間を回転自在な切り換え部（５４）と、当該切り換え部（５４）を回転操作する操作レバー（５３）とを備え、
前記ばね筒（２５）の外周側には、前記ピン（５１）より弁（２７）側に前記切り換え部（５４）と対向する係合部（２５ｂ）が設けられ、
前記切り換え部（５４）の外周面には、前記ピン（５１）から所定距離となる位置に設けられるとともに、前記非伝達状態となる角度で前記係合部（２５ｂ）に当接することにより、前記ピン（５１）の前記弁（２７）側への移動を規制する非伝達用外周面部（５５）と、前記ピン（５１）から前記所定距離より短い距離となる位置に設けられ、前記伝達状態となる角度で、前記係合部（２５ｂ）に対向する伝達用外周面部（５６Ａ）とが備えられていることを特徴とする。 According to a third aspect of the present invention, in the pressure regulating valve according to the second aspect, the switching means (50) includes a handle (52) for switching between the transmission state and the non-transmission state.
The handle (52) is engaged with the end of the pin (51) penetrating the spring cylinder (25), and the angle at which the pin is in the transmission state and the angle at which the pin (51) is not in the transmission state. A switching portion (54) that can freely rotate between and an operation lever (53) that rotates the switching portion (54).
On the outer peripheral side of the spring cylinder (25), an engaging portion (25b) is provided on the valve (27) side of the pin (51) so as to face the switching portion (54).
An outer peripheral surface of the switching portion (54) is provided at a position at a predetermined distance from the pin (51), and abuts on the engagement portion (25b) at an angle at which the non-transmission state is established. A non-transmission outer peripheral surface portion (55) for restricting the movement of the pin (51) toward the valve (27), and a position that is shorter than the predetermined distance from the pin (51); And an outer peripheral surface portion (56A) for transmission facing the engaging portion (25b) at an angle.

なお、上記における括弧内の符号は、図面において対応する要素を便宜的に表記したものであり、したがって本発明は図面上の記載に限定されるものではない。これは、「特許請求の範囲」の記載についても同様である。   In addition, the code | symbol in the bracket | parenthesis in the above expresses the corresponding element in drawing for convenience, Therefore, this invention is not limited to description on drawing. The same applies to the description of “Claims”.

請求項１に記載の発明によれば、低圧用の第２のばねの荷重を用いた低圧状態での調圧と、高圧用の第１のばねの荷重を用いた高圧状態での調圧とを行うことができる。
すなわち、第２のばねの荷重を用いた低圧状態での調圧においては、切り替え手段により、第１の伝達部材の弁側への移動を規制することにより非伝達状態として、第１のばねの荷重が弁に伝達されない状態で、圧縮量調整手段により第１のばねおよび第２のばねの圧縮量を調整する。第１のばねと第２のばねとは圧縮量調整手段により押し付けられて圧縮される。
この際に、第１のばねの荷重は、切り替え手段により、弁に伝達されず、第２のばねの荷重だけが第２の伝達部材を介して、弁に作用する。したがって、調圧弁は、第２のばねの圧縮量に基づいた荷重による圧力調整を行う。 According to the first aspect of the present invention, the pressure adjustment in the low pressure state using the load of the second spring for low pressure, the pressure adjustment in the high pressure state using the load of the first spring for high pressure, It can be performed.
That is, in the pressure adjustment in the low pressure state using the load of the second spring, the switching means restricts the movement of the first transmission member to the valve side, thereby setting the non-transmission state to the first spring. In a state where the load is not transmitted to the valve, the compression amounts of the first spring and the second spring are adjusted by the compression amount adjusting means. The first spring and the second spring are pressed and compressed by the compression amount adjusting means.
At this time, the load of the first spring is not transmitted to the valve by the switching means, and only the load of the second spring acts on the valve via the second transmission member. Therefore, the pressure regulating valve performs pressure adjustment with a load based on the compression amount of the second spring.

一方、第１のばねの荷重を用いた高圧状態での調圧においては、切り替え手段により、第１の伝達部材の弁側への移動が可能な伝達状態とすることにより、第１のばねの荷重が弁に伝達される。第２のばねの荷重は、高圧状態での調圧においても弁に伝達される。
この高圧状態では、圧縮量調整手段により、第１のばねと第２のばねが圧縮されるが、第２のばねが、低圧状態での圧縮調整手段での圧縮範囲を越えて圧縮された状態となることがない。したがって、本発明の高圧状態では、従来のように第２のばねが低圧状態での使用の圧縮範囲を越えて大きく圧縮されることがないので、強度上不利となることがない。 On the other hand, in the pressure adjustment in the high pressure state using the load of the first spring, the switching means makes the transmission state in which the movement of the first transmission member to the valve side is possible. Load is transmitted to the valve. The load of the second spring is transmitted to the valve even during pressure adjustment in a high pressure state.
In this high pressure state, the first spring and the second spring are compressed by the compression amount adjusting means, but the second spring is compressed beyond the compression range of the compression adjusting means in the low pressure state. It will never be. Therefore, in the high pressure state of the present invention, since the second spring is not greatly compressed beyond the compression range of use in the low pressure state as in the prior art, there is no disadvantage in strength.

また、従来のように第２のばねが低圧状態での使用から高圧状態での使用となる際に、低圧状態での最も圧縮された状態よりさらに圧縮されるようなことがないので、低圧状態での圧縮範囲内での圧縮に好適な仕様値の第２のばねを使用することができる。したがって、例えば、第１のばねの内部に第２のばねが配置される場合に、第１のばねは内部に配置される第２のばねが必要以上に大きくなることがないので、高圧状態に適した仕様値の第１のばねを用いることができる。   Further, when the second spring is changed from being used in a low pressure state to being used in a high pressure state as in the prior art, it is not compressed further than the most compressed state in the low pressure state. It is possible to use a second spring having a specification value suitable for compression within the compression range at. Therefore, for example, when the second spring is arranged inside the first spring, the second spring arranged inside the first spring does not become unnecessarily large. A first spring of suitable specification value can be used.

また、必要以上に大きなばね定数の第１のばねや第２のばねが使用されることがなく、適切な仕様値（たとえば、適切なばね定数）の第１のばねや第２のばねを使用できるので、圧縮量調整手段での少しの第１のばねおよび第２のばねの圧縮量の調整で、ばね荷重が大きく変化することがなく、調圧の微調整を容易に行うことができる。   In addition, the first spring and the second spring having a spring constant larger than necessary are not used, and the first spring and the second spring having an appropriate specification value (for example, an appropriate spring constant) are used. Therefore, the adjustment of the compression amount of the first spring and the second spring by a small amount of compression amount adjustment means does not greatly change the spring load, and fine adjustment of the pressure adjustment can be easily performed.

請求項２に記載の発明によれば、伝達状態の際に前記弁側への移動が許容され、非伝達状態の際に前記弁側への移動が規制されるピンが、ばね筒と第２の伝達部材の長穴を通るとともに第１の伝達部材の貫通孔を通っており、当該ピンが第１の伝達部材の貫通孔に嵌合して第１の伝達部材だけがピンと一体に移動可能となっている。
しがって、第２の伝達部材は、常時第２のばねの付勢力を弁側に伝達可能な状態で、第１の伝達部材だけが、伝達状態では弁側に移動可能となり、非伝達状態では弁側への移動が規制されることにより、伝達状態の場合にだけ、第１の伝達部材が第１のばねの付勢力を弁に伝達可能となる。
以上のことから、ピンを用いた簡単な構成により、同軸上に配置される第１の伝達部材と第２の伝達部材とのうちの第１の伝達部材だけを伝達状態と非伝達状態とに切り換えることができる。 According to the second aspect of the present invention, the pin that is allowed to move to the valve side in the transmission state and is restricted from moving to the valve side in the non-transmission state includes the spring cylinder and the second pin. Passes through the long hole of the transmission member and the through hole of the first transmission member, and the pin fits into the through hole of the first transmission member so that only the first transmission member can move integrally with the pin. It has become.
Therefore, the second transmission member can always transmit the urging force of the second spring to the valve side, and only the first transmission member can move to the valve side in the transmission state. In the state, the movement toward the valve side is restricted, so that the first transmission member can transmit the urging force of the first spring to the valve only in the transmission state.
From the above, with a simple configuration using pins, only the first transmission member of the first transmission member and the second transmission member arranged on the same axis is set to the transmission state and the non-transmission state. Can be switched.

請求項３に記載の発明によれば、ハンドルの操作レバーを操作して、ピンの端部に係合して当該ピンを回転中心として回転可能な切り換え部を、前記非伝達状態とする角度とすると、切り換え部の外周面の非伝達用外周面部がばね筒の前記ピンが貫通する部位よりも弁側に設けられた係合部に当接する。
この状態では、ピンより弁側の係合部とピンを回転中心とする切り替え部とが当接していることにより、ピンの弁側への移動が規制されることになる。なお、ピンから切り換え部の非伝達用外周面部までの所定距離は、例えば、弁が弁座に当接し、第１の伝達部材が最も弁側に配置された状態での第１の伝達部材に嵌合するピンから係合部までの距離より長い距離である。
一方、切り換え部を伝達状態とする角度では、係合部に切り換え部の非伝達用外周面部が対向した状態となり、この際には、例えば、係合部と非伝達外周面とが接触しない状態となる。すなわち、ピンから非伝達外周面までの距離は、前記所定距離より短く、さらに、前記弁が弁座に当接し、第１の伝達部材が最も弁側に配置された状態での第１の伝達部材に嵌合するピンから係合部までの距離以下となる。
以上のことからバンドルの操作レバーで切り換え部を回転させるだけの簡単な操作で、例えば、低圧散布を行う状態と、高圧散布を行う状態を切り換えることが可能となる。 According to the third aspect of the present invention, an angle at which the switching portion that is engaged with the end portion of the pin and can rotate around the pin by operating the operation lever of the handle is set to the non-transmission state Then, the non-transmission outer peripheral surface portion of the outer peripheral surface of the switching portion comes into contact with the engaging portion provided on the valve side with respect to the portion of the spring cylinder through which the pin passes.
In this state, the engagement of the valve side with respect to the pin and the switching unit having the pin as the rotation center are in contact with each other, so that the movement of the pin to the valve side is restricted. The predetermined distance from the pin to the non-transmission outer peripheral surface portion of the switching portion is, for example, the first transmission member in a state where the valve is in contact with the valve seat and the first transmission member is disposed on the most valve side. The distance is longer than the distance from the fitting pin to the engaging portion.
On the other hand, at the angle at which the switching portion is in the transmission state, the non-transmission outer peripheral surface portion of the switching portion faces the engagement portion, and in this case, for example, the engagement portion and the non-transmission outer peripheral surface are not in contact with each other It becomes. That is, the distance from the pin to the non-transmission outer peripheral surface is shorter than the predetermined distance, and the first transmission in a state where the valve is in contact with the valve seat and the first transmission member is disposed on the most valve side. It becomes below the distance from the pin fitted to a member to an engaging part.
From the above, it is possible to switch, for example, a state in which low-pressure spraying is performed and a state in which high-pressure spraying is performed with a simple operation by simply rotating the switching unit with the operation lever of the bundle.

本発明の第１の実施の形態に係る調圧弁を示す図であって、低圧散布時の調圧弁を示す側面図である。It is a figure which shows the pressure regulation valve which concerns on the 1st Embodiment of this invention, Comprising: It is a side view which shows the pressure regulation valve at the time of low pressure spraying. 同、高圧散布時の調圧弁を示す側面図である。It is a side view which shows the pressure regulation valve at the time of high-pressure spraying same as the above. 同、図１のＡ−Ａ線に沿う断面図である。It is sectional drawing which follows the AA line of FIG. 同、図２のＢ−Ｂ線に沿う断面図である。It is sectional drawing which follows the BB line of FIG. 同、ばね筒を示す断面図である。It is sectional drawing which shows a spring cylinder same as the above. 同、第２カラーを示す断面図である。It is sectional drawing which shows a 2nd color | collar similarly. 同、第１カラーを示す断面図である。It is sectional drawing which shows a 1st color similarly. 本発明の第２の実の施形態に係る調圧弁を示す図であって、低圧散布時の調圧弁を示す断面図である。It is a figure which shows the pressure regulating valve which concerns on the 2nd actual embodiment of this invention, Comprising: It is sectional drawing which shows the pressure regulating valve at the time of low pressure spraying. 同、高圧散布時の調圧弁を示す断面図である。It is sectional drawing which shows the pressure regulation valve at the time of high pressure spraying same as the above. 従来の調圧弁を示す断面図である。It is sectional drawing which shows the conventional pressure regulation valve.

以下、図面を参照しながら、本発明の第１の実施の形態について説明する。
図１〜図７は本発明の第１の実施の形態に係る調圧弁を示す図であって、図１は低圧散布時の調圧弁を示す側面図であり、図２は高圧散布時の調圧弁を示す側面図であり、図３は低圧散布時の調圧弁を示す断面図であり、図４は高圧散布時の調圧弁を示す断面図であり、図５はばね筒を示す断面図であり、図６は第２カラーを示す断面図であり、図７は第１カラーを示す断面図である。 The first embodiment of the present invention will be described below with reference to the drawings.
1 to 7 are views showing the pressure regulating valve according to the first embodiment of the present invention. FIG. 1 is a side view showing the pressure regulating valve during low-pressure spraying, and FIG. 2 is a pressure regulating valve during high-pressure spraying. FIG. 3 is a sectional view showing a pressure regulating valve during low-pressure spraying, FIG. 4 is a sectional view showing the pressure regulating valve during high-pressure spraying, and FIG. 5 is a sectional view showing a spring cylinder. FIG. 6 is a sectional view showing the second collar, and FIG. 7 is a sectional view showing the first collar.

図１〜図４に示すように、この調圧弁は、流入口２１と余液口２２と接続口２３とが形成されたボディ２４と、このボディ２４の接続口２３に接合されるばね筒２５と、ボディ２４の流入口２１に設けられる弁座２６と、この弁座２６に対向して配置される弁２７と、ばね筒２５内に配置される高圧用の第１のばねとしての皿ばね２８と、同じくばね筒２５内に配置される低圧用の第２のばねとしての圧縮コイルばね２９と、これら皿ばね２８および圧縮コイルばね２９の荷重を弁２７に伝達する伝達手段３０と、皿ばね２８および圧縮コイルばね２９の圧縮量を調整する圧縮量調整手段４０と、皿ばね２８の荷重を弁２７に伝達する状態と伝達しない状態を切り替える切り替え手段５０とを備えている。   As shown in FIGS. 1 to 4, the pressure regulating valve includes a body 24 in which an inflow port 21, an excess liquid port 22, and a connection port 23 are formed, and a spring cylinder 25 joined to the connection port 23 of the body 24. A valve seat 26 provided at the inlet 21 of the body 24, a valve 27 disposed opposite to the valve seat 26, and a disc spring as a high pressure first spring disposed in the spring cylinder 25. 28, a compression coil spring 29 as a second low-pressure spring, also disposed in the spring cylinder 25, a transmission means 30 for transmitting the load of the disc spring 28 and the compression coil spring 29 to the valve 27, and a disc A compression amount adjusting means 40 for adjusting the compression amount of the spring 28 and the compression coil spring 29 and a switching means 50 for switching between a state in which the load of the disc spring 28 is transmitted to the valve 27 and a state in which the load is not transmitted are provided.

ボディ２４の流入口２１は下側に開口しており、この流入口２１が図示しないポンプの吐出口に接続されるようになっている。この例において、ポンプは、薬剤散布用のもので、例えば、薬液を吐出するものとなっている。また、この例の調圧弁では、後述のように低圧散布（例えば、０．５ＭＰａレベル）用の低圧状態と高圧散布（例えば、３ＭＰａレベル）用の高圧状態とに切り替えられることにより、薬剤散布を低圧散布と高圧散布とに切り換えることができるようになっている。
余液口２２は、略水平方向を向くように開口しており、また接続口２３は、流入口２１と同軸に配置されるとともに、流入口２１と逆方向の上側に開口している。 The inflow port 21 of the body 24 opens downward, and the inflow port 21 is connected to a discharge port of a pump (not shown). In this example, the pump is for spraying medicine, and for example, discharges a liquid medicine. Moreover, in the pressure regulating valve of this example, as described later, by switching between a low pressure state for low pressure spraying (for example, 0.5 MPa level) and a high pressure state for high pressure spraying (for example, 3 MPa level), drug spraying is performed. It is possible to switch between low-pressure spraying and high-pressure spraying.
The surplus liquid port 22 is opened so as to face substantially in the horizontal direction, and the connection port 23 is arranged coaxially with the inflow port 21 and is opened on the upper side in the opposite direction to the inflow port 21.

ボディ２４の接続口２３側の内部には、ガイド筒３１が設けられている。ガイド筒３１は、概略円筒状に形成されており、ボディ２４の内部において、接続口２３から流入口２１に向かって延びている。このガイド筒３１は、上端部に形成された大径部が、ボディ２４の接続口２３に形成された段差部に係止されるとともに、ばね筒２５の下端面によって接続口２３から抜け出るのを阻止されることにより、ボディ２４に固定されている。ガイド筒３１の大径部の外周面と、接続口２３の内周面との間にはＯリング６１が設けられており、これによりガイド筒３１の外周を通って液体が接続口２３から外部に漏れないようになっている。   A guide cylinder 31 is provided inside the connection port 23 side of the body 24. The guide tube 31 is formed in a substantially cylindrical shape, and extends from the connection port 23 toward the inflow port 21 inside the body 24. The guide tube 31 has a large-diameter portion formed at the upper end portion engaged with a stepped portion formed at the connection port 23 of the body 24 and is prevented from coming out of the connection port 23 by the lower end surface of the spring tube 25. By being blocked, it is fixed to the body 24. An O-ring 61 is provided between the outer peripheral surface of the large-diameter portion of the guide tube 31 and the inner peripheral surface of the connection port 23, so that liquid passes through the outer periphery of the guide tube 31 from the connection port 23 to the outside. It is designed not to leak.

ガイド筒３１内には、円柱状の弁保持部材３２が上下移動自在に嵌合されている。ガイド筒３１の内周面と弁保持部材３２の外周面との間には、Ｏリング６２，６２が設けられ、これらの間の液密が保たれている。弁保持部材３２の先端（下端）には、弁２７がボルト６５により固定されている。
また、ガイド筒３１内には、弁保持部材３２の上側に緩衝部材としての防振ゴム３３が配置され、さらに防振ゴム３３の上側にばね受３４が配置されている。これらの防振ゴム３３およびばね受け３４もガイド筒３１内を上下移動自在に設けられている。 A cylindrical valve holding member 32 is fitted in the guide tube 31 so as to be movable up and down. Between the inner peripheral surface of the guide cylinder 31 and the outer peripheral surface of the valve holding member 32, O-rings 62 and 62 are provided, and the liquid tightness between them is maintained. The valve 27 is fixed to the front end (lower end) of the valve holding member 32 with a bolt 65.
Further, in the guide tube 31, a vibration isolating rubber 33 as a buffer member is disposed above the valve holding member 32, and a spring receiver 34 is disposed above the vibration isolating rubber 33. These anti-vibration rubber 33 and spring receiver 34 are also provided in the guide cylinder 31 so as to be movable up and down.

ばね筒２５は、ガイド筒３１と同軸に配置されているとともに、連通した状態となっている。ばね受け３４は、ばね筒２５およびガイド筒３１に渡って配置されている。ばね筒２５の内径とガイド筒３１の上端部の内径とは同じ径に形成されており、ばね受３４は、ばね筒２５とガイド筒３１とに跨って上下移動するようになっている。   The spring cylinder 25 is arranged coaxially with the guide cylinder 31 and is in a communicating state. The spring receiver 34 is disposed across the spring cylinder 25 and the guide cylinder 31. The inner diameter of the spring cylinder 25 and the inner diameter of the upper end portion of the guide cylinder 31 are formed to be the same diameter, and the spring receiver 34 moves up and down across the spring cylinder 25 and the guide cylinder 31.

ばね筒２５は、有蓋円筒状に形成されており、蓋部分の中央部には、ねじ孔（雌ねじ）２５ａが形成され、ねじ孔（雌ねじ）２５ａに握り４１の雄ねじ部４２が螺合されている。ねじ孔２５ａは、ばね筒２５の本体部分（円筒部分）と同軸に配置されている。
ばね筒２５内には、ばね筒２５の内径より少し小さい外径の皿ばね２８が配置されている。皿ばね２８は、複数個が交互に表裏を反対にして上下に積層されている。皿ばね２８の内側には、圧縮コイルばね２９が配置されている。圧縮コイルばね２９の外径は、皿ばね２８の内径より少し小さく設定されている。 The spring cylinder 25 is formed in a covered cylindrical shape. A screw hole (female screw) 25a is formed in the center of the lid part, and the male screw part 42 of the grip 41 is screwed into the screw hole (female screw) 25a. Yes. The screw hole 25 a is disposed coaxially with the main body portion (cylindrical portion) of the spring cylinder 25.
A disc spring 28 having an outer diameter slightly smaller than the inner diameter of the spring cylinder 25 is disposed in the spring cylinder 25. A plurality of disc springs 28 are stacked one above the other with the front and back opposite to each other. A compression coil spring 29 is disposed inside the disc spring 28. The outer diameter of the compression coil spring 29 is set slightly smaller than the inner diameter of the disc spring 28.

皿ばね２８および圧縮コイルばね２９の軸方向は、ばね筒２５の軸方向と同じとなっているとともに、ばね筒２５と皿ばね２８と圧縮コイルばね２９とは、同軸に配置されている。複数の皿ばね２８全体の自由高さの方が圧縮コイルばね２９の自由高さより少し長くなるように設定されている。
ばね筒２５の開放側端部には、拡径した板状のフランジ部２５ｂが形成されているとともに、ボディ２４の接続口２３側の端部には、板状のフランジ部２４ｂが形成されており、これらのフランジ部２５ｂ、２４ｂを貫通してボルト７１がポンプの吐出部等にねじ込まれることにより、ばね筒２５とボディ２４とが一体的に固定されるとともに、調圧弁がポンプの吐出部等に取り付けられる。 The axial directions of the disc spring 28 and the compression coil spring 29 are the same as the axial direction of the spring cylinder 25, and the spring cylinder 25, the disc spring 28, and the compression coil spring 29 are arranged coaxially. The total free height of the plurality of disc springs 28 is set to be slightly longer than the free height of the compression coil spring 29.
A plate-like flange portion 25b having an enlarged diameter is formed at the open end portion of the spring cylinder 25, and a plate-like flange portion 24b is formed at the end portion of the body 24 on the connection port 23 side. The bolt 71 is screwed into the pump discharge portion and the like through the flange portions 25b and 24b, so that the spring cylinder 25 and the body 24 are fixed integrally, and the pressure regulating valve is connected to the pump discharge portion. Etc.

図５に示すように、ばね筒２５の下端部の左右には、後述のピン５１が貫通する長穴２５ｃが形成されている。長穴２５ｃは、その長さ方向がばね筒２５の軸方向と平行となっている。２つの長穴２５ｃの中心を繋ぐ線分は、ばね筒２５の軸心を通る（軸心と交差する）ようになっている。
ばね筒２５の内部には、上述のように皿ばね２８と圧縮コイルばね２９とが配置されるが、皿ばね２８および圧縮コイルばね２９の上側には、ばね筒２５の内径より少し小さな外径の円板状のばね押部材４３が配置されている。 As shown in FIG. 5, elongated holes 25 c through which pins 51 described later pass are formed on the left and right sides of the lower end portion of the spring cylinder 25. The long hole 25 c has a length direction parallel to the axial direction of the spring cylinder 25. A line segment connecting the centers of the two long holes 25c passes through the axis of the spring cylinder 25 (crosses the axis).
As described above, the disc spring 28 and the compression coil spring 29 are disposed inside the spring cylinder 25, and an outer diameter slightly smaller than the inner diameter of the spring cylinder 25 is provided above the disc spring 28 and the compression coil spring 29. A disc-shaped spring pressing member 43 is arranged.

ばね押部材４３は、ばね筒２５内でこのばね筒２５の軸方向に移動自在に配置されており、その下面に皿ばね２８および圧縮コイルばね２９の上端が当接している。ばね押部材４３の下面中央部には下方に突出する突出部が形成されており、この突出部の外周に圧縮コイルばね２９の上端部の内周が嵌合している。握り４１を回転してねじ込むことにより、ばね押部材４３を上側から押して、ばね筒２５の蓋側から皿ばね２８および圧縮コイルばね２９側にばね押部材４３を移動させ、これにより皿ばね２８および圧縮コイルばね２９を圧縮するようになっている。したがって、ばね筒２５の蓋部分に螺合する雄ねじ部４２を有する握り４１とばね押部材４３とにより、圧縮量調整手段４０が構成されている。
圧縮量調整手段４０は、上述のように略同じ自由高さを有する皿ばね２８と圧縮コイルばね２９とを、略同じ圧縮量だけ同時に圧縮する構成となっている。 The spring pressing member 43 is disposed in the spring cylinder 25 so as to be movable in the axial direction of the spring cylinder 25, and the upper ends of the disc spring 28 and the compression coil spring 29 are in contact with the lower surfaces thereof. A projecting portion projecting downward is formed at the center of the lower surface of the spring pressing member 43, and the inner periphery of the upper end portion of the compression coil spring 29 is fitted to the outer periphery of the projecting portion. By rotating and gripping the grip 41, the spring pressing member 43 is pushed from the upper side, and the spring pressing member 43 is moved from the lid side of the spring tube 25 to the disc spring 28 and the compression coil spring 29 side. The compression coil spring 29 is compressed. Therefore, the compression amount adjusting means 40 is constituted by the grip 41 having the male thread portion 42 screwed into the lid portion of the spring cylinder 25 and the spring pressing member 43.
The compression amount adjusting means 40 is configured to simultaneously compress the disc spring 28 and the compression coil spring 29 having substantially the same free height as described above by substantially the same compression amount.

ばね筒２５内のボディ２４側には、筒状の第１カラー３５と筒状の第２カラー３６とがばね筒２５と同軸に配置されている。第１カラー３５は、その外径がばね筒２５の内径より少し小さいものとされ、ばね筒２５の軸方向に沿って移動自在となっている。第１カラー３５の上端には、皿ばね２８の下端が当接するようになっている。第１カラー３５の内側には、第１カラー３５の内径より少し小さい外径を有する第２カラー３６が配置されている。第２カラー３６は、第１カラー３５の内側で第１カラー３５の軸方向に沿って移動自在となっている。第２カラー３６の上端には、中間ばね受３６Ａを介して圧縮コイルばね２９の下端が当接するようになっている。すなわち、中間ばね受３６Ａの上面および下面にそれぞれ、圧縮コイルばね２９の下端および第２カラー３６の上端が当接している。中間ばね受３６Ａの上下面の中央部にはそれぞれ、上方および下方に突出する突出部が形成されており、上側の突出部の外周に圧縮コイルばね２９の下端部の内周が嵌合しているとともに、下側の突出部の外周に第２カラー３６の上端部の内周が嵌合している。中間ばね受３６Ａの外周は、皿ばね２８の内径より少し小さく設定されており、皿ばね２８の下端部の内側に配置されている。   A cylindrical first collar 35 and a cylindrical second collar 36 are disposed coaxially with the spring cylinder 25 on the body 24 side in the spring cylinder 25. The first collar 35 has an outer diameter that is slightly smaller than the inner diameter of the spring cylinder 25, and is movable along the axial direction of the spring cylinder 25. The lower end of the disc spring 28 is in contact with the upper end of the first collar 35. A second collar 36 having an outer diameter slightly smaller than the inner diameter of the first collar 35 is disposed inside the first collar 35. The second collar 36 is movable along the axial direction of the first collar 35 inside the first collar 35. The lower end of the compression coil spring 29 is in contact with the upper end of the second collar 36 via an intermediate spring receiver 36A. That is, the lower end of the compression coil spring 29 and the upper end of the second collar 36 are in contact with the upper surface and the lower surface of the intermediate spring receiver 36A, respectively. Protrusions projecting upward and downward are respectively formed at the center portions of the upper and lower surfaces of the intermediate spring receiver 36A, and the inner periphery of the lower end of the compression coil spring 29 is fitted to the outer periphery of the upper protrusion. In addition, the inner periphery of the upper end portion of the second collar 36 is fitted to the outer periphery of the lower protrusion. The outer periphery of the intermediate spring receiver 36 </ b> A is set slightly smaller than the inner diameter of the disc spring 28, and is disposed inside the lower end portion of the disc spring 28.

ばね筒２５内の第１カラー３５および第２カラー３６の下側には、前述のばね受３４が配置されている。ばね受３４は、肉厚の円板状に形成されており、その上面の中央部には、円柱状の突出部が形成されている。ばね受３４の上面の外周部分には、第１カラー３５の下端が当接するようになっている。ばね受３４の上面の第１カラー３５が当接する部分より内側に第２カラー３６の下端が当接するようになっている。ばね受３４の突出部は、第２カラー３６の下端部の内側に挿入されている。   The above-described spring receiver 34 is disposed below the first collar 35 and the second collar 36 in the spring cylinder 25. The spring receiver 34 is formed in a thick disk shape, and a cylindrical protrusion is formed at the center of the upper surface thereof. The lower end of the first collar 35 is in contact with the outer peripheral portion of the upper surface of the spring receiver 34. The lower end of the second collar 36 abuts on the inner side of the portion of the upper surface of the spring receiver 34 where the first collar 35 abuts. The protruding portion of the spring receiver 34 is inserted inside the lower end portion of the second collar 36.

このような構成において、握り４１をねじ込んで、ばね押部材４３を下降させると、皿ばね２８および圧縮コイルばね２９が圧縮される。皿ばね２８および圧縮コイルばね２９においては、ばね筒２５の軸方向に沿った付勢力（ばね荷重）が生じることになる。これにより、皿ばね２８の下端に当接する第１カラー３５に下向きの付勢力が作用し、圧縮コイルばね２９の下端に当接する第２カラー３６に下向きの付勢力が作用する。これらの第１カラー３５および第２カラー３６の付勢力によりばね受３４が下側に押され、ばね受３４から防振ゴム３３、弁保持部材３２を介して弁２７が弁座２６に押し付けられた状態となる。   In such a configuration, when the grip 41 is screwed and the spring pressing member 43 is lowered, the disc spring 28 and the compression coil spring 29 are compressed. In the disc spring 28 and the compression coil spring 29, an urging force (spring load) along the axial direction of the spring cylinder 25 is generated. As a result, a downward biasing force acts on the first collar 35 that contacts the lower end of the disc spring 28, and a downward biasing force acts on the second collar 36 that contacts the lower end of the compression coil spring 29. The spring bearing 34 is pushed downward by the urging force of the first collar 35 and the second collar 36, and the valve 27 is pushed against the valve seat 26 from the spring bearing 34 through the vibration isolating rubber 33 and the valve holding member 32. It becomes a state.

以上のことから、第１カラー３５、第２カラー３６、ばね受３４、防振ゴム３３および弁保持部材３２は、皿ばね２８および圧縮コイルばね２９の荷重を弁２７に伝達する伝達手段３０を構成している。
また、第１カラー３５は、第１のばねである皿ばね２８の荷重をばね受３４等の部材を介して弁２７に伝達する第１の伝達部材を構成し、第２カラー３６は、第２のばねである圧縮コイルばね２９の荷重をばね受３４等の部材を介して弁２７に伝達する第２の伝達部材を構成している。 From the above, the first collar 35, the second collar 36, the spring receiver 34, the anti-vibration rubber 33 and the valve holding member 32 provide the transmission means 30 for transmitting the load of the disc spring 28 and the compression coil spring 29 to the valve 27. It is composed.
The first collar 35 constitutes a first transmission member that transmits the load of the disc spring 28, which is a first spring, to the valve 27 through a member such as a spring receiver 34, and the second collar 36 has a first collar 36. A second transmission member is configured to transmit the load of the compression coil spring 29, which is the second spring, to the valve 27 through a member such as a spring receiver 34.

図７に示すように、第１カラー３５には、ばね筒２５の長穴２５ｃに対向する位置に、この長穴２５ｃと連通するように円形の貫通孔３５ａが形成されている。すなわち、筒状の第１カラー３５には、左右側部にそれぞれ貫通孔３５ａが形成されている。
また、第１カラー３５の貫通孔３５ａの形成位置は、第１カラー３５が後述のようにばね受３４に当接した状態（高圧散布のための高圧状態）では、ばね筒２５の長穴２５ｃの下部側に対向する位置に位置するようになっている。 As shown in FIG. 7, a circular through hole 35 a is formed in the first collar 35 at a position facing the long hole 25 c of the spring cylinder 25 so as to communicate with the long hole 25 c. That is, the cylindrical first collar 35 is formed with through holes 35a on the left and right sides.
In addition, the through hole 35a of the first collar 35 is formed at a long hole 25c in the spring cylinder 25 when the first collar 35 is in contact with the spring receiver 34 as described later (a high pressure state for high pressure spraying). It is located in the position which opposes the lower part side.

図６に示すように、第２カラー３６には、ばね筒２５の長穴２５ｃと、第１カラー３５の貫通孔３５ａとの両方に対向する長穴３６ａが形成されている。すなわち、筒状の第２カラー３６には、左右側部のそれぞれに長穴３６ａが形成されている。第２カラー３６の長穴３６ａは、ばね筒２５の長穴２５ｃと重なった状態となっており、第２カラー３６の長穴３６ａとばね筒２５の長穴２５ｃとは、上端部および下端部の位置が略同じとなっている。   As shown in FIG. 6, the second collar 36 is formed with a long hole 36 a that faces both the long hole 25 c of the spring cylinder 25 and the through hole 35 a of the first collar 35. That is, the cylindrical second collar 36 is formed with a long hole 36a on each of the left and right side portions. The elongated hole 36a of the second collar 36 overlaps the elongated hole 25c of the spring cylinder 25. The elongated hole 36a of the second collar 36 and the elongated hole 25c of the spring cylinder 25 have an upper end portion and a lower end portion. The positions of are substantially the same.

これらのばね筒２５の左右側部の長穴２５ｃ、第１カラー３５の左右側部の円形の貫通孔３５ａおよび第２カラー３６の左右側部の長穴３６ａには、円柱状のピン５１が挿入されており、このピン５１の左右端部は、ばね筒２５の外周面から外側に突出している。ピン５１の外径は、第１カラー３５の貫通孔３５ａより僅かに小さい外径とされ、かつ、ばね筒２５の長穴２５ｃの幅（短径）および第２カラー３６の長穴３６ａの幅（短径）より僅かに小さくされている。このピン５１をばね筒２５および第２カラー３６の長穴３６ａの長さ（長径）の範囲内で上下動させた場合に、ばね筒２５および第２カラー３６に対して第１カラー３５がピン５１とともに上下動する構成となっている。   A cylindrical pin 51 is provided in the elongated holes 25 c on the left and right sides of the spring cylinder 25, the circular through holes 35 a on the left and right sides of the first collar 35, and the elongated holes 36 a on the left and right sides of the second collar 36. The left and right end portions of the pin 51 protrude outward from the outer peripheral surface of the spring cylinder 25. The outer diameter of the pin 51 is slightly smaller than the through hole 35 a of the first collar 35, and the width (short diameter) of the long hole 25 c of the spring cylinder 25 and the width of the long hole 36 a of the second collar 36. It is slightly smaller than (minor axis). When the pin 51 is moved up and down within the length (long diameter) of the long hole 36 a of the spring cylinder 25 and the second collar 36, the first collar 35 is pinned with respect to the spring cylinder 25 and the second collar 36. 51 is configured to move up and down together.

ピン５１のばね筒２５から外側に突出する左右の端部には、ハンドル５２の基端部が回動自在に取り付けられている。ハンドル５２は、棒状の操作レバー５３と、操作レバー５３の基端部から二股に分岐されピン５１の両端部にそれぞれ取り付けられる一対のカム部（切り換え部）５４とを備えている。   A base end portion of the handle 52 is rotatably attached to left and right end portions of the pin 51 that protrude outward from the spring cylinder 25. The handle 52 includes a rod-like operation lever 53 and a pair of cam portions (switching portions) 54 that are bifurcated from the base end portion of the operation lever 53 and attached to both end portions of the pin 51.

カム部５４は、その下側となる外周面がカムとして機能するもので、操作レバー５３を持ち上げた時に、その下側の外周面（平面）がばね筒２５のフランジ部（係合部）２５ｂの上面に押し付けられるようになっている。
左右のカム部５４は、同形状に形成され、左右のカム部５４の下側の外周面には、図１に示すように、後述する低圧状態（非伝達状態）において、フランジ部２５ｂの上面に当接する低圧当接部（非伝達用外周面部）５５と、図２に示すように、後述する高圧状態と低圧状態との切替時において、フランジ部２５ｂの上面に当接する高低切替当接部５６とが周方向に隣接して配置されている。低圧当接部５５は、略平面状とされ、高低切替当接部５６は、所定の曲率半径の円弧面上に形成されている。高低切替当接部５６を境として、低圧当接部５５の反対側となるカム部５４の外周面部分が伝達用外周面部５６Ａとなる。 The cam portion 54 has a lower outer peripheral surface that functions as a cam. When the operation lever 53 is lifted, the lower outer peripheral surface (plane) is the flange portion (engagement portion) 25 b of the spring cylinder 25. It is designed to be pressed against the top surface.
The left and right cam portions 54 are formed in the same shape, and on the lower outer peripheral surface of the left and right cam portions 54, as shown in FIG. 1, the upper surface of the flange portion 25 b in a low pressure state (non-transmission state) described later. 2 and a high / low switching contact portion that contacts the upper surface of the flange portion 25b when switching between a high pressure state and a low pressure state, which will be described later, as shown in FIG. 56 are arranged adjacent to each other in the circumferential direction. The low-pressure contact portion 55 has a substantially flat shape, and the height switching contact portion 56 is formed on an arc surface having a predetermined radius of curvature. With the height switching contact portion 56 as a boundary, the outer peripheral surface portion of the cam portion 54 on the opposite side of the low pressure contact portion 55 becomes the transmission outer peripheral surface portion 56A.

フランジ部２５ｂに低圧当接部５５が当接するカム部５４の角度が非伝達状態でカム部５４の角度となり、フランジ部２５ｂに伝達用外周面部５６Ａが対向した状態となるカム部５４の角度が伝達状態でのカム部５４の角度となる。
また、カム部５４において、ピン５１の位置から低圧当接部５５までの距離は、ピン５１から伝達用外周面部５６Ａまでの距離より長くなっている。ピン５１の位置から低圧当接部５５までの距離（所定距離）は、弁２７が弁座２６に当接し、第１のカラー３５が最も弁２７側に配置された状態での第１のカラー３５に嵌合するピン５１からフランジ部２５ｂまでの距離より長い。また、ピン５１から伝達用外周面部５６Ａまでの距離は、上述のピン５１からフランジ部２５ｂまでの距離以下となっている。 The angle of the cam portion 54 with which the low-pressure contact portion 55 contacts the flange portion 25b becomes the angle of the cam portion 54 in the non-transmitting state, and the angle of the cam portion 54 where the transmitting outer peripheral surface portion 56A faces the flange portion 25b. This is the angle of the cam portion 54 in the transmission state.
In the cam portion 54, the distance from the pin 51 to the low-pressure contact portion 55 is longer than the distance from the pin 51 to the transmission outer peripheral surface portion 56A. The distance (predetermined distance) from the position of the pin 51 to the low pressure contact portion 55 is the first collar when the valve 27 is in contact with the valve seat 26 and the first collar 35 is disposed closest to the valve 27. It is longer than the distance from the pin 51 fitted to 35 to the flange portion 25b. Moreover, the distance from the pin 51 to the outer peripheral surface portion 56A for transmission is equal to or less than the distance from the pin 51 to the flange portion 25b.

また、左右のカム部５４の中央部には、ピン孔５７が形成されており、これらのピン孔５７にそれぞれ、ピン５１の両端部が挿入され、抜け止めされている。ハンドル５２は、操作レバー５３を操作することにより、ピン５１が挿入されたピン孔５７を中心として回動する。
そして、ハンドル５２のカム部５４の低圧当接部がフランジ部２５ｂ上面に当接する状態が低圧状態となり、この低圧当接部がフランジ部２５ｂ上面に当接した状態からこのフランジ部２５ｂ上面に高低切替当接部５６がフランジ部２５ｂ上面に当接する状態を越えるように回転させた状態が高圧状態となる。
したがって、ハンドル５２を上述の低圧状態と高圧状態との間で回動するように操作することにより、低圧状態と高圧状態とを切り替えることができる。 In addition, pin holes 57 are formed in the center portions of the left and right cam portions 54, and both end portions of the pins 51 are inserted into these pin holes 57 to prevent them from coming off. The handle 52 rotates around the pin hole 57 into which the pin 51 is inserted by operating the operation lever 53.
The state in which the low pressure contact portion of the cam portion 54 of the handle 52 is in contact with the upper surface of the flange portion 25b is a low pressure state, and the state in which the low pressure contact portion is in contact with the upper surface of the flange portion 25b is A state where the switching contact portion 56 is rotated so as to exceed the contact state with the upper surface of the flange portion 25b is a high pressure state.
Therefore, by operating the handle 52 to rotate between the low pressure state and the high pressure state described above, the low pressure state and the high pressure state can be switched.

また、ハンドル５２のカム部５４が上述の低圧状態と高圧状態との間を回動した際に、ピン孔５７およびピン孔５７に挿入されたピン５１は、ばね筒２５および第２カラー３６の長穴２５ｃ、３６ａに沿って上下動するが、ピン５１の位置は、高圧状態より低圧状態の方がより高い位置（ボディ２４や弁座２６から離れる位置）となっている。   When the cam portion 54 of the handle 52 rotates between the low pressure state and the high pressure state described above, the pin hole 57 and the pin 51 inserted into the pin hole 57 are connected to the spring cylinder 25 and the second collar 36. Although it moves up and down along the long holes 25c and 36a, the position of the pin 51 is higher in the low pressure state than the high pressure state (position away from the body 24 and the valve seat 26).

図１および図３に示すように、低圧状態においては、平面状の低圧当接部５５が平面状のフランジ部２５ｂ上面に当接しているとともに、これら平面部分に直交する方向に皿ばね２８の付勢力が作用するので、ハンドル５２が操作されなければ、安定した状態となっており、ハンドル５２が操作されないかぎり低圧状態を維持するようになっている。   As shown in FIG. 1 and FIG. 3, in the low pressure state, the flat low pressure contact portion 55 is in contact with the upper surface of the flat flange portion 25b, and the disc spring 28 extends in a direction perpendicular to these flat portions. Since the urging force acts, if the handle 52 is not operated, the state is stable, and the low pressure state is maintained unless the handle 52 is operated.

また、低圧状態では、高圧状態よりピン５１の位置が上側となるので、ピン５１と一体に上下動する第１カラー３５が高圧状態より上側の位置で保持された状態となる。
これにより、低圧状態では、例えば、弁２７、弁保持部材３２、防振ゴム３３、ばね受３４が順に当接するとともに、弁座２６に弁２７が当接した状態では、ばね受３４から第１カラー３５が少し離れた状態となるとともに、下側への移動が規制された状態となる。 Further, in the low pressure state, the position of the pin 51 is higher than in the high pressure state, so that the first collar 35 that moves up and down integrally with the pin 51 is held in a position above the high pressure state.
Thereby, in the low pressure state, for example, the valve 27, the valve holding member 32, the vibration isolating rubber 33, and the spring receiver 34 are in contact with each other in order, and in the state in which the valve 27 is in contact with the valve seat 26, The collar 35 is in a state of being slightly separated, and the downward movement is restricted.

このように、第１カラー３５の下側への移動が規制されることにより、皿ばね２８の付勢力が第１カラー３５に作用しても、第１カラー３５から付勢力が、ばね受３４側に伝達されることがなく、皿ばね２８の荷重は弁２７に作用しない。この状態では、圧縮コイルばね２９の付勢力だけが第２カラー３６からばね受３４、防振ゴム３３、弁保持部材３２を介して弁２７に伝達され、弁２７を弁座２６に押し付ける状態となる。   Thus, even if the urging force of the disc spring 28 acts on the first collar 35 by restricting the downward movement of the first collar 35, the urging force is applied from the first collar 35 to the spring receiver 34. The load of the disc spring 28 does not act on the valve 27. In this state, only the urging force of the compression coil spring 29 is transmitted from the second collar 36 to the valve 27 via the spring receiver 34, the vibration isolating rubber 33, and the valve holding member 32, and the valve 27 is pressed against the valve seat 26. Become.

一方、高圧状態では、低圧当接部がフランジ部２５ｂ上面に当接した状態から当該フランジ部２５ｂ上面に高低切替当接部５６がフランジ部２５ｂ上面に当接する状態を越えるように回動させた状態となることにより、第１カラー３５の下側への移動の規制が解除された状態となり、皿ばね２８の付勢力により第１カラー３５が弁座２６側（下側）に移動可能となる。
これにより、高圧状態では、皿ばね２８および圧縮コイルばね２９の付勢力が第１カラー３５および第２カラー３６からばね受３４、防振ゴム３３、弁保持部材３２を介して弁２７に伝達され、弁２７が弁座２６に押し付けられる状態となる。 On the other hand, in the high pressure state, the low pressure contact portion is rotated from the state where the low pressure contact portion is in contact with the upper surface of the flange portion 25b so as to exceed the state where the height switching contact portion 56 is in contact with the upper surface of the flange portion 25b. By entering the state, the restriction on the downward movement of the first collar 35 is released, and the first collar 35 can be moved to the valve seat 26 side (downward) by the biasing force of the disc spring 28. .
Thereby, in a high pressure state, the urging force of the disc spring 28 and the compression coil spring 29 is transmitted from the first collar 35 and the second collar 36 to the valve 27 via the spring receiver 34, the vibration isolating rubber 33, and the valve holding member 32. The valve 27 is pressed against the valve seat 26.

以上のような調圧弁においては、ハンドル５２の操作レバー５３を上下に回動操作することにより、低圧散布用の低圧状態と、高圧散布用の高圧状態とを簡単に切り替えられるようになっており、この例では、操作レバー５３を起こして立てるように操作し、ハンドル５２のカム部５４の低圧当接部５５をフランジ部２５ｂの上面に当接した状態とすると、第１カラー３５が上述のように少し上側に移動するとともに、下側へ（弁側へ）の移動が規制された状態となる。   In the pressure regulating valve as described above, the operation lever 53 of the handle 52 is turned up and down to easily switch between a low pressure state for low pressure spraying and a high pressure state for high pressure spraying. In this example, when the operation lever 53 is raised and operated so that the low pressure contact portion 55 of the cam portion 54 of the handle 52 is in contact with the upper surface of the flange portion 25b, the first collar 35 is In this manner, the movement toward the upper side and the movement toward the lower side (to the valve side) are restricted.

これにより、上述のように皿ばね２８の荷重は弁２７に伝達されない。この状態では、圧縮コイルばね２９の荷重のみが第２カラー３６、ばね受３４等を介して弁２７に伝達され、弁２７が弁座２６側に付勢される。この状態では、圧縮コイルばね２９の荷重だけが弁２７に伝達されるとともに、圧縮コイルばね２９の強さが、皿ばね２８の強さより低くなっていることから、小さな荷重が弁２７に作用し、低圧散布用の低圧状態となる。   As a result, the load of the disc spring 28 is not transmitted to the valve 27 as described above. In this state, only the load of the compression coil spring 29 is transmitted to the valve 27 via the second collar 36, the spring receiver 34, etc., and the valve 27 is urged toward the valve seat 26. In this state, only the load of the compression coil spring 29 is transmitted to the valve 27, and the strength of the compression coil spring 29 is lower than the strength of the disc spring 28, so that a small load acts on the valve 27. It becomes a low pressure state for low pressure spraying.

一方、低圧状態からハンドル５２の操作レバー５３を伏せるように操作し、ハンドル５２のカム部５４の高低切替当接部５６がフランジ部２５ｂの上面に当接した状態を越えるようにすると、第１カラー３５が下側への移動の規制が解除され、第１カラー３５が下側に移動し、ばね受３４に当接した状態となる。この際にポンプが作動していなければ、第１カラー３５、ばね受３４等を介して弁２７を弁座２６に押し付けた状態となる。   On the other hand, if the operation lever 53 of the handle 52 is operated to bend down from the low pressure state so that the height switching contact portion 56 of the cam portion 54 of the handle 52 exceeds the contact state with the upper surface of the flange portion 25b, the first The restriction on the downward movement of the collar 35 is released, the first collar 35 moves downward, and comes into contact with the spring receiver 34. If the pump is not operating at this time, the valve 27 is pressed against the valve seat 26 via the first collar 35, the spring receiver 34, and the like.

この状態では、弁２７には、低圧状態で作用していなかった皿ばね２８の荷重が伝達されて作用し、圧縮コイルばね２９の荷重とそれより強い皿ばね２８の荷重が作用することになり、高圧散布が可能な高圧状態となる。
なお、高圧状態および低圧状態のいずれにおいても、握り４１のねじ込み量、すなわち、握り４１のねじ込み量に基づいて皿ばね２８および圧縮コイルばね２９の圧縮量が決まり、この圧縮量とばね定数に基づいて、弁２７に作用する荷重が決まることになる。 In this state, the load of the disc spring 28 that was not acting in the low pressure state is transmitted and acted on the valve 27, and the load of the compression coil spring 29 and the load of the disc spring 28 stronger than that are acted on. It becomes a high-pressure state in which high-pressure spraying is possible.
In both the high pressure state and the low pressure state, the compression amount of the disc spring 28 and the compression coil spring 29 is determined based on the screwing amount of the grip 41, that is, the screwing amount of the grip 41, and based on the compression amount and the spring constant. Thus, the load acting on the valve 27 is determined.

以上のことから、第１カラー３５は、弁２７に皿ばね２８の荷重を伝達する伝達状態と、皿ばね２８の荷重を弁２７に伝達しない非伝達状態とにハンドル５２によって切り替え可能となっている。したがって、操作レバー５３、カム部５４を備えるハンドル５２とピン５１とが切り替え手段５０を構成している。
この例では、従来と同様に高圧状態では、皿ばね２８の荷重と圧縮コイルばね２９の荷重とが両方作用することになるが、高圧状態における皿ばね２８および圧縮コイルばね２９の圧縮量の範囲と、低圧状態における皿ばね２８および圧縮コイルばね２９の圧縮量の範囲とは、ほぼ同じとなっている。したがって、従来のように高圧状態において、圧縮コイルばね２９が低圧状態で最も圧縮された状態より、さらに圧縮された状態となることがなく、圧縮コイルばね２９は、高圧状態であっても、低圧状態での使用範囲内での圧縮量以上に圧縮されることがない。 From the above, the first collar 35 can be switched by the handle 52 between a transmission state in which the load of the disc spring 28 is transmitted to the valve 27 and a non-transmission state in which the load of the disc spring 28 is not transmitted to the valve 27. Yes. Therefore, the operation lever 53, the handle 52 including the cam portion 54, and the pin 51 constitute the switching means 50.
In this example, both the load of the disc spring 28 and the load of the compression coil spring 29 act in the high pressure state as in the conventional case, but the compression amount range of the disc spring 28 and the compression coil spring 29 in the high pressure state. And the range of the compression amount of the disc spring 28 and the compression coil spring 29 in a low pressure state is substantially the same. Therefore, in the high pressure state, the compression coil spring 29 is not further compressed than the compression state most compressed in the low pressure state, and the compression coil spring 29 is low in pressure even in the high pressure state. It is not compressed more than the compression amount within the use range in the state.

なお、皿ばね２８は、低圧状態において、下端側が少し上に持ち上げられた状態となることから、低圧状態における最大圧縮量が、高圧状態における最大圧縮量より少し大きくなるが、皿ばね２８の仕様に影響を与えるほどのものではない。
このように高圧状態でも低圧状態でも、皿ばね２８および圧縮コイルばね２９の圧縮量の範囲が略同じで、最も大きな圧縮量も同じなので、従来のように、圧縮コイルばね２９が高圧状態で、低圧状態での最も大きな圧縮量よりさらに大きな圧縮量まで圧縮されることがない。 In addition, since the disc spring 28 is in a state where the lower end side is slightly raised in the low pressure state, the maximum compression amount in the low pressure state is slightly larger than the maximum compression amount in the high pressure state. It is not so much as to affect.
As described above, since the range of the compression amount of the disc spring 28 and the compression coil spring 29 is substantially the same in both the high pressure state and the low pressure state, and the largest compression amount is the same, the compression coil spring 29 is in the high pressure state as in the prior art. It is not compressed to a compression amount larger than the maximum compression amount in the low pressure state.

したがって、圧縮コイルばね２９および皿ばね２８とも、それらの使用状態に適した仕様値のばねを選択して使用することができる。
したがって、従来、圧縮コイルばね２９や皿ばね２８が使用時に必要とされる圧縮率よりも高い圧縮率に対応した仕様のものを使用していたのに対して、使用される範囲に適した圧縮コイルばね２９や皿ばね２８が用いられることにより、調圧において、少しの握り４１のねじ込みで、圧力が大きく異なってしまうようなことがなく、微調整を容易に行うことが可能となる。
また、低圧散布と高圧散布を切り換えられる従来の調圧弁に比較して低圧縮率となる仕様値の圧縮コイルばね２９および皿ばね２８を用いることができるので、ポンプの吐出側に接続されたノズルを閉としてポンプを作動するとともに、調圧弁の無負荷状態として、ポンプから吐出される薬液を全て余液口２２から流出させる状態とした際、すなわち全余水時における圧力変化を小さくすることができる。 Therefore, for the compression coil spring 29 and the disc spring 28, a spring having a specification value suitable for the use state thereof can be selected and used.
Therefore, the compression coil spring 29 and the disc spring 28 have conventionally been used with specifications corresponding to a compression rate higher than the compression rate required at the time of use, whereas the compression suitable for the range to be used is used. By using the coil spring 29 and the disc spring 28, fine adjustment can be easily performed without causing a large difference in pressure when the grip 41 is screwed in a little during pressure adjustment.
In addition, since the compression coil spring 29 and the disc spring 28 having a specification value having a low compression ratio can be used as compared with a conventional pressure regulating valve that can switch between low pressure spraying and high pressure spraying, a nozzle connected to the discharge side of the pump When the pump is operated with the pressure closed and the pressure regulating valve is in a no-load state, all the chemical liquid discharged from the pump is allowed to flow out from the residual liquid port 22, that is, the pressure change at the time of total residual water can be reduced. it can.

図８および図９は、本発明の第２の実施の形態に係る調圧弁を示す図であって、図８は低圧散布を行う低圧状態の調圧弁を示す断面図、図９は高圧散布を行う高圧状態の調圧弁を示す断面図である。
この第２の実施の形態の調圧弁は、ピン５８の形状と、第２カラー３８の形状が異なる以外は、第１の実施の形態の調圧弁と同様の構成を有するものとなっている。
以下に、第１の実施の形態と異なる構成となる部分だけを説明し、同様の構成となる部分の説明を省略する。 8 and 9 are views showing a pressure regulating valve according to the second embodiment of the present invention. FIG. 8 is a sectional view showing a pressure regulating valve in a low pressure state for performing low pressure spraying, and FIG. It is sectional drawing which shows the pressure regulation valve of the high pressure state to perform.
The pressure regulating valve of the second embodiment has the same configuration as the pressure regulating valve of the first embodiment except that the shape of the pin 58 and the shape of the second collar 38 are different.
Below, only the part which becomes a different structure from 1st Embodiment is demonstrated, and description of the part which becomes the same structure is abbreviate | omitted.

図８および図９に示すように、第２の実施の形態におけるピン５８は、左右に分離された状態となっており、第１の実施の形態のピン５１のように第２カラー３６にピンが貫通された状態となっていない。
したがって、第２の実の施形態の第２カラー３８には、ピン５８を貫通するための長穴が形成されず、第２カラー３８は、外周面および内周面に孔の無い円筒状の部材となっている。
第１カラー３５には、第１の実施の形態と同様の貫通孔３５ａが形成されている。また、ばね筒２５にも第１の実施の形態と同様の長穴２５ｃが形成されている。 As shown in FIGS. 8 and 9, the pin 58 in the second embodiment is separated into the left and right, and the pin 58 is pinned to the second collar 36 like the pin 51 in the first embodiment. Is not penetrated.
Therefore, the second collar 38 in the second embodiment is not formed with a long hole for penetrating the pin 58, and the second collar 38 has a cylindrical shape with no holes on the outer peripheral surface and the inner peripheral surface. It is a member.
The first collar 35 is formed with a through hole 35a similar to that of the first embodiment. The spring cylinder 25 is also formed with a long hole 25c similar to that of the first embodiment.

左右に分割された状態のピン５８はそれぞれ、先端部が第１カラー３５の貫通孔３５ａに挿入されて当該貫通孔３５ａに固定された状態となっている。
また、ピン５８のばね筒２５から外側に突出した部分は、第１の実施の形態と同様にハンドル５２の左右のカム部５４のピン孔５７に挿入されて固定された状態となっている。 Each of the pins 58 in a state of being divided into left and right is in a state where the tip portion is inserted into the through hole 35a of the first collar 35 and fixed to the through hole 35a.
Further, the portion of the pin 58 that protrudes outward from the spring cylinder 25 is in a state of being inserted into and fixed to the pin holes 57 of the left and right cam portions 54 of the handle 52 as in the first embodiment.

この調圧弁は、ハンドル５２を操作することにより、第２カラー３６に影響を与えることなく、図９に示すように、第１カラー３６を皿ばね２８の荷重を弁２７に伝達可能な伝達状態と、図８に示すように、弁２７に伝達不可能な非伝達状態とに切り替え可能となり、第１の実施の形態と同様の作用効果を得ることができる。   As shown in FIG. 9, the pressure regulating valve can transmit the load of the disc spring 28 to the valve 27 without affecting the second collar 36 by operating the handle 52. As shown in FIG. 8, it is possible to switch to a non-transmission state incapable of being transmitted to the valve 27, and it is possible to obtain the same effect as that of the first embodiment.

２５ ばね筒
２５ｂ フランジ部（係合部）
２５ｃ 長穴
２７ 弁
２８ 皿ばね（圧縮ばね、第１のばね）
２９ 圧縮コイルばね（圧縮ばね、第２のばね）
３５ 第１カラー（第１の伝達部材）
３５ａ 貫通孔
３６ 第２カラー（第２の伝達部材）
３６ａ 長穴
４０ 圧縮量調整手段
５０ 切り替え手段
５１ ピン
５２ ハンドル
５３ 操作レバー
５４ 切り換え部
５５ 低圧用当接部（非伝達用外周面部）
５６Ａ 伝達用外周面部 25 Spring cylinder 25b Flange part (engagement part)
25c long hole 27 valve 28 disc spring (compression spring, first spring)
29 Compression coil spring (compression spring, second spring)
35 First collar (first transmission member)
35a Through-hole 36 2nd collar (second transmission member)
36a Long hole 40 Compression amount adjusting means 50 Switching means 51 Pin 52 Handle 53 Operation lever 54 Switching portion 55 Low pressure contact portion (non-transmission outer peripheral surface portion)
56A Outer peripheral surface for transmission

Claims (3)

圧縮量調整手段（４０）により圧縮量を調整可能な圧縮ばね（２８，２９）の荷重を弁（２７）に作用させつつ当該弁（２７）と弁座（２６）との間に液体を通過させて圧力を生じさせる調圧弁において、
前記圧縮ばね（２８，２９）として、第１のばね（２８）と、当該第１のばね（２８）より低い圧力を生じさせる第２のばね（２９）とを備え、
前記弁（２７）と前記第１のばね（２８）との間に前記弁（２７）に前記第１のばね（２８）の荷重を伝達させる第１の伝達部材（３５）が設けられ、前記弁（２７）と前記第２のばね（２９）との間に前記弁（２７）に前記第２のばね（２９）の荷重を伝達させる第２の伝達部材（３６）が設けられ、
前記第１の伝達部材（３５）には、当該第１の伝達部材（３５）を前記弁（２７）側に移動可能として前記第１のばね（２８）の荷重を前記弁（２７）に伝達可能とする伝達状態と、当該第１の伝達部材（３５）の弁（２７）側への移動を規制して前記第１のばね（２８）の荷重を前記弁（２７）に伝達不可とする非伝達状態とのいずれかとする切り替え手段（５０）が設けられていることを特徴とする調圧弁。 Liquid is passed between the valve (27) and the valve seat (26) while the load of the compression springs (28, 29) whose compression amount can be adjusted by the compression amount adjusting means (40) is applied to the valve (27). In a pressure regulating valve that generates pressure,
The compression springs (28, 29) include a first spring (28) and a second spring (29) that generates a lower pressure than the first spring (28),
A first transmission member (35) for transmitting the load of the first spring (28) to the valve (27) is provided between the valve (27) and the first spring (28), and A second transmission member (36) for transmitting the load of the second spring (29) to the valve (27) is provided between the valve (27) and the second spring (29),
In the first transmission member (35), the load of the first spring (28) is transmitted to the valve (27) by allowing the first transmission member (35) to move toward the valve (27). The transmission state to be enabled and the movement of the first transmission member (35) to the valve (27) side are restricted so that the load of the first spring (28) cannot be transmitted to the valve (27). A pressure regulating valve, characterized in that switching means (50) for switching between the non-transmission state and the non-transmission state is provided. 前記第１のばね（２８）および前記第２のばね（２９）と、前記第１の伝達部材（３５）および第２の伝達部材（３６）とを軸方向に並べた状態で収容する筒状のばね筒（２５）を備え、
前記第１のばね（２８）と、前記第２のばね（２９）とが内外に重なるように同軸上に配置され、
第１の伝達部材（３５）と第２の伝達部材（３６）とが内外に重なるように同軸上に配置され、
前記切り換え手段は、前記ばね筒（２５）と前記第１の伝達部材と前記第２の伝達部材とを貫通するとともに、前記伝達状態の際に前記弁（２７）側への移動が許容され、前記非伝達状態の際に前記弁側の移動が規制されるピン（５１）を備え、
前記ばね筒（２５）および第２の伝達部材（３６）には、前記ピン（５１）が貫通するとともに前記ピン（５１）の前記弁（２７）側への移動を許容する長穴（２５ｃ、３６ａ）が形成され、
第１の伝達部材（３５）には、当該第１の伝達部材が前記ピンと一体に移動するように前記ピンが貫通した状態で嵌合する貫通孔（３５ａ）が形成されていることを特徴とする請求項１に記載の調圧弁。 A cylindrical shape that houses the first spring (28) and the second spring (29), and the first transmission member (35) and the second transmission member (36) in an axially aligned state. The spring cylinder (25)
The first spring (28) and the second spring (29) are arranged coaxially so as to overlap inside and outside,
The first transmission member (35) and the second transmission member (36) are arranged coaxially so as to overlap inside and outside,
The switching means penetrates the spring cylinder (25), the first transmission member and the second transmission member, and is allowed to move toward the valve (27) in the transmission state. A pin (51) that restricts movement of the valve side in the non-transmission state;
In the spring cylinder (25) and the second transmission member (36), the pin (51) penetrates and a long hole (25c, which allows the pin (51) to move to the valve (27) side). 36a) is formed,
The first transmission member (35) is formed with a through hole (35a) that fits in a state where the pin penetrates so that the first transmission member moves integrally with the pin. The pressure regulating valve according to claim 1. 前記切り替え手段（５０）は、前記伝達状態と前記非伝達状態とを切り替えるハンドル（５２）を備え、
前記ハンドル（５２）には、前記ばね筒（２５）を貫通した前記ピン（５１）の端部に係合して当該ピンを回転中心とし前記伝達状態となる角度と前記非伝達状態となる角度との間を回転自在な切り換え部（５４）と、当該切り換え部（５４）を回転操作する操作レバー（５３）とを備え、
前記ばね筒（２５）の外周側には、前記ピン（５１）より弁（２７）側に前記切り換え部（５４）と対向する係合部（２５ｂ）が設けられ、
前記切り換え部（５４）の外周面には、前記ピン（５１）から所定距離となる位置に設けられるとともに、前記非伝達状態となる角度で前記係合部（２５ｂ）に当接することにより、前記ピン（５１）の前記弁（２７）側への移動を規制する非伝達用外周面部（５５）と、前記ピン（５１）から前記所定距離より短い距離となる位置に設けられ、前記伝達状態となる角度で、前記係合部（２５ｂ）に対向する伝達用外周面部（５６Ａ）とが備えられていることを特徴とする請求項２に記載の調圧弁 The switching means (50) includes a handle (52) for switching between the transmission state and the non-transmission state,
The handle (52) is engaged with the end of the pin (51) penetrating the spring cylinder (25), and the angle at which the pin is in the transmission state and the angle at which the pin (51) is not in the transmission state. A switching portion (54) that can freely rotate between and an operation lever (53) that rotates the switching portion (54).
On the outer peripheral side of the spring cylinder (25), an engaging portion (25b) is provided on the valve (27) side of the pin (51) so as to face the switching portion (54).
An outer peripheral surface of the switching portion (54) is provided at a position at a predetermined distance from the pin (51), and abuts on the engagement portion (25b) at an angle at which the non-transmission state is established. A non-transmission outer peripheral surface portion (55) for restricting the movement of the pin (51) toward the valve (27), and a position that is shorter than the predetermined distance from the pin (51); The pressure regulating valve according to claim 2, further comprising a transmission outer peripheral surface portion (56A) facing the engaging portion (25b) at an angle of
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