JPH0117749Y2 - - Google Patents
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- Publication number
- JPH0117749Y2 JPH0117749Y2 JP16147484U JP16147484U JPH0117749Y2 JP H0117749 Y2 JPH0117749 Y2 JP H0117749Y2 JP 16147484 U JP16147484 U JP 16147484U JP 16147484 U JP16147484 U JP 16147484U JP H0117749 Y2 JPH0117749 Y2 JP H0117749Y2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- valve seat
- head
- pressure
- valve head
- 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.)
- Expired
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- 239000012530 fluid Substances 0.000 claims description 22
- 238000011144 upstream manufacturing Methods 0.000 claims description 9
- 230000007423 decrease Effects 0.000 description 13
- 238000013459 approach Methods 0.000 description 7
- 235000014676 Phragmites communis Nutrition 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 2
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- Lift Valve (AREA)
- Details Of Valves (AREA)
Description
【考案の詳細な説明】
（産業上の利用分野）
本考案は自動車のエンジン等に用いられる流量
制御弁に関する。[Detailed Description of the Invention] (Field of Industrial Application) The present invention relates to a flow control valve used in automobile engines and the like.
（従来技術）
一般に、この種流量制御弁は弁の上流側と下流
側の圧力差に応じて自動的に開閉弁するようにな
つており、その従来例としては、例えば、第８図
に示すようなものがある。この流量制御弁にあつ
ては、流入口４１と流出口４２との間に形成され
る流路内において、リード弁４３の上流側に絞り
弁４４を備え、上記流入口４１から流出口４２へ
と流れる空気等の流体の流量を自由に制御し得る
ようになつている。すなわち、上記絞り弁４４
は、ダイアフラム室４５に供給される作動流体の
信号圧力によつて作動するダイヤフラム４６に連
結された弁体４７と、該弁体４７の弁頭４８が着
座する弁座４９とよりなつている。従つてダイア
フラム室４５内に供給される作動流体の信号圧力
を増すことにより、同ダイアフラム室４５内の圧
力が上昇すると、ダイアフラム４６が圧縮スプリ
ング５０の弾発力に抗して押下げられるため、該
ダイアフラム４６に連結された弁体４７も同時に
押下げられ、流体の流量が制御される。(Prior Art) Generally, this type of flow control valve is designed to automatically open and close depending on the pressure difference between the upstream side and the downstream side of the valve. There is something like that. In this flow rate control valve, a throttle valve 44 is provided on the upstream side of the reed valve 43 in the flow path formed between the inlet 41 and the outlet 42, and the flow from the inlet 41 to the outlet 42 is The flow rate of fluid such as air can be freely controlled. That is, the throttle valve 44
consists of a valve body 47 connected to a diaphragm 46 that is actuated by a signal pressure of a working fluid supplied to a diaphragm chamber 45, and a valve seat 49 on which a valve head 48 of the valve body 47 is seated. Therefore, when the pressure inside the diaphragm chamber 45 increases by increasing the signal pressure of the working fluid supplied into the diaphragm chamber 45, the diaphragm 46 is pushed down against the elastic force of the compression spring 50. A valve body 47 connected to the diaphragm 46 is also pressed down at the same time, and the flow rate of the fluid is controlled.
しかし、上記流量制御弁にあつては、弁体４７
の弁頭４８が弁座４９に近づくにつれ、弁頭４８
と弁座４９との間を流れる空気の流速が増し圧力
が低下するので、弁頭４８の弁座当接面４８ａ側
に加わる圧力が小さくなる。これに対して、弁頭
４８の上記弁座当接面４８ａと反対の面（以下、
反弁座当接面と称する）４８ｂ側に加わる圧力は
変化しないため、第９図に示すように弁頭４８の
反弁座当接面４８ｂ側に加わる圧力P1と弁座当
接面４８ａ側に加わる圧力P2とのバランスがく
ずれ、弁頭４８の反弁座当接面４８ｂ側に加わる
圧力P1の方が大きくなる。この結果、弁体４７
を閉じる方向に作用する力すなわち圧力P1の方
が大きくなつて、急激に弁体４７が閉じてしま
い、第１０図に示すように、広範囲の信号圧力に
わたつて絞り弁４４を作動させ、空気の流量を制
御することができないといつた問題点があつた。 However, in the above flow control valve, the valve body 47
As the valve head 48 approaches the valve seat 49, the valve head 48
Since the flow velocity of the air flowing between the valve seat 49 and the valve seat 49 increases and the pressure decreases, the pressure applied to the valve seat abutting surface 48a side of the valve head 48 decreases. On the other hand, the surface of the valve head 48 opposite to the valve seat contact surface 48a (hereinafter referred to as
Since the pressure applied to the side 48b (referred to as the anti-valve seat abutting surface) does not change, as shown in FIG . The balance with the pressure P 2 applied to the side is lost, and the pressure P 1 applied to the side opposite to the valve seat contact surface 48b of the valve head 48 becomes larger. As a result, the valve body 47
The force acting in the closing direction, that is, the pressure P1 , becomes larger, and the valve body 47 suddenly closes.As shown in FIG. 10, the throttle valve 44 is operated over a wide range of signal pressures, There was a problem that the flow rate of air could not be controlled.
この対策として、本出願人は、第１１図及び第
１２図にすような流量制御弁を既に提案してい
る。この流量制御弁は、第６図に示すものと同一
部分については同一符号を付して説明すると、弁
頭４８が弁座４９に近づいて弁座当接面４８ａに
加わる圧力が低下した際、弁頭４８の反弁座当接
面４８ｂを密封的に覆うと共に当該弁頭４８の外
周側面４８ｃと微小間隙ｇを有して対面する弁箱
５１側に支持されたラビリンス室５２によつて生
じるラビリンス効果を利用して、反弁座当接面４
８ｂに加わる圧力を減少させ、弁頭４８の両面に
加わる圧力のバランスをとつて、弁体４７の動作
を安定させると共に、広範囲にわたつて空気等の
流体の流量を滑らかに制御することができるよう
になつている。 As a countermeasure to this problem, the applicant has already proposed a flow control valve as shown in FIGS. 11 and 12. This flow control valve will be described with the same reference numerals used for the same parts as shown in FIG. 6. When the valve head 48 approaches the valve seat 49 and the pressure applied to the valve seat contact surface 48a decreases, This is caused by the labyrinth chamber 52 that sealingly covers the anti-valve seat contact surface 48b of the valve head 48 and is supported on the side of the valve box 51 that faces the outer peripheral side surface 48c of the valve head 48 with a minute gap g. Using the labyrinth effect, the anti-valve seat contact surface 4
By reducing the pressure applied to 8b and balancing the pressure applied to both sides of the valve head 48, the operation of the valve body 47 can be stabilized, and the flow rate of fluid such as air can be smoothly controlled over a wide range. It's becoming like that.
（考案が解決しようとする問題点）
しかし、斯かる従来例の場合には、第１２図に
示すように、弁体４７の弁頭４８が弁座４９に近
づき、弁頭４８と弁座４９の隙間が微小になる
と、この隙間を流れる空気の流速がかなり速くな
り圧力が大きく低下するので、弁頭４８の弁座当
接面４８ａ側に加わる圧力P2が大幅に低下する。
これに対して、弁頭４８の反弁座当接面４８ｂ側
に加わる圧力は、ラビリンス室５２によつて生じ
るラビリンス効果により、弁頭４８の上流側に位
置する空気の圧力P1より小さくなる。ところが、
弁頭４８の弁座当接面４８ａ側に加わる圧力P2
の低下の方が、弁頭４８の反弁座当接面４８ｂ側
に加わる圧力P3の低下より大きいため、弁頭４
８の反弁座当接面４８ｂ側に加わる圧力P3と弁
座当接面４８ａ側に加わる圧力P2とのバランス
がくずれ、弁頭４８の反弁座当接面４８ｂ側に加
わる圧力P3の方が大きくなる。この結果、弁体
４７を閉じる方向に作用する力すなわち圧力P3
の方が大きくなつて、急激に弁体４８が閉じてし
まい、第１３図に示すように、流量がある程度の
値（図中Ｃ点）まで減少してくると、それ以上少
ない流量の制御が行なえないという問題点があ
る。(Problems to be Solved by the Invention) However, in the case of such a conventional example, as shown in FIG. When the gap becomes minute, the flow rate of air flowing through this gap becomes considerably faster and the pressure decreases significantly, so the pressure P 2 applied to the valve seat abutting surface 48a side of the valve head 48 decreases significantly.
On the other hand, the pressure applied to the side of the valve head 48 opposite to the valve seat contact surface 48b becomes smaller than the pressure P 1 of the air located on the upstream side of the valve head 48 due to the labyrinth effect caused by the labyrinth chamber 52. . However,
Pressure P 2 applied to the valve seat contact surface 48a side of the valve head 48
Since the decrease in the pressure P3 applied to the side of the valve head 48 opposite to the valve seat contact surface 48b is greater than the decrease in the pressure P3 applied to the side of the valve head 48 opposite to the valve seat contact surface 48b, the
The balance between the pressure P 3 applied to the anti-valve seat contact surface 48b side of the valve head 48 and the pressure P 2 applied to the valve seat contact surface 48a side of the valve head 48 is lost, and the pressure P applied to the anti-valve seat contact surface 48b side of the valve head 48 is lost. 3 is larger. As a result, a force acting in the direction of closing the valve body 47, that is, a pressure P 3
becomes larger, and the valve body 48 suddenly closes, and as shown in FIG. 13, when the flow rate decreases to a certain value (point C in the figure), it is no longer possible to control a smaller flow rate. The problem is that it cannot be done.
本考案は、従来技術の斯かる問題点を解決する
ためになされたもので、その目的とするところ
は、弁頭と弁座の隙間が微小になつた場合でも、
流量の制御を滑らかに行なうことができ、最終的
にすべての範囲にわたつて空気等の流体の流量を
滑らかに制御することができるようにした流量制
御弁を提供することにある。 The present invention was devised to solve the problems of the prior art, and its purpose is to provide a valve that can be used even when the gap between the valve head and the valve seat becomes minute.
It is an object of the present invention to provide a flow rate control valve that can smoothly control the flow rate and finally can smoothly control the flow rate of a fluid such as air over the entire range.
（問題点を解決するための手段）
そこで、本考案は、上記の目的を達成するため
に、弁箱内に設けられた弁座と、前記弁座の上流
側に配置され、ダイアフラム室に供給される作動
流体により前記弁座と協働して開閉弁する弁頭を
備えた弁体と、前記弁頭の反弁座当接面を密封的
に覆うと共に当該弁頭の外周側面と微小間隙を有
して対面する前記弁箱側に支持されるラビリンス
室とを備えてなる流量制御弁において、前記弁頭
の弁座当接面を円錐形状に形成すると共に、前記
弁座を弾性体により形成し、前記弁座を構成する
弾性体の一部を内側に突出させて環状のフインを
設け、該フインに切欠部を設けるように構成され
ている。(Means for Solving the Problems) Therefore, in order to achieve the above object, the present invention provides a valve seat provided in a valve box, a valve seat disposed upstream of the valve seat, and a valve seat disposed upstream of the valve seat that is supplied to the diaphragm chamber. a valve body having a valve head that opens and closes the valve in cooperation with the valve seat by the working fluid that is applied to the valve; and a labyrinth chamber supported by the valve box side facing each other, the valve seat contacting surface of the valve head is formed into a conical shape, and the valve seat is made of an elastic body. A part of the elastic body constituting the valve seat is formed to protrude inward to provide an annular fin, and a notch is provided in the fin.
（実施例）
以下に本考案を図示の実施例に基づいて説明す
る。第１図乃至第６図において、１は流量制御弁
本体であり、この流量制御弁本体１は弁箱２と、
該弁箱２の上下に被着された上部カバー３と下部
カバー４とよりなつている。上記流量制御弁本体
１は、流入口５と流出口６とを備えており、流路
７中に絞り弁８が配置されていて、この絞り弁８
は弁箱１０付き弁体９と弁座１１からなつてい
る。さらにその下流側にはリード弁１２の弁座１
３とストツパー１４とが配設されており、該弁座
１３とストツパー１４との間にはリード１５が装
備されている。(Example) The present invention will be explained below based on the illustrated example. 1 to 6, 1 is a flow control valve main body, and this flow control valve main body 1 has a valve box 2,
It consists of an upper cover 3 and a lower cover 4 attached to the top and bottom of the valve box 2. The flow control valve main body 1 includes an inlet 5 and an outlet 6, and a throttle valve 8 is disposed in a flow path 7.
consists of a valve body 9 with a valve body 10 and a valve seat 11. Furthermore, on the downstream side is the valve seat 1 of the reed valve 12.
3 and a stopper 14 are disposed, and a lead 15 is provided between the valve seat 13 and the stopper 14.
前記絞り弁８の弁体９は弁軸１６を備えてお
り、この弁軸１６は軸受１７及び軸シール１８を
介して弁箱２の支持部１９に支持されている。こ
の弁軸１６の上端は、弁箱２と上部カバー３との
間に挾着されたダイアフラム２０に、上下のセン
ターデイスク２１，２２を介して連結されてい
る。このダイアフラム２０は、外部の圧力源より
供給口２３を介してダイアフラム室２４に供給さ
れる作動流体の信号圧力により、圧縮スプリング
２５の弾発力に抗して押下げられ、前記弁頭１０
を弁座１１に着座させるようになつている。前記
弁箱２には、ダイアフラム２０の下面側を大気に
開放する開放孔２６が穿設されており、該ダイア
フラム２０に連結された弁頭１０は、ダイアフラ
ム室２４内の圧力と大気圧との差圧によつて作動
される。 The valve body 9 of the throttle valve 8 includes a valve shaft 16 , and the valve shaft 16 is supported by a support portion 19 of the valve body 2 via a bearing 17 and a shaft seal 18 . The upper end of this valve shaft 16 is connected to a diaphragm 20 that is clamped between the valve box 2 and the upper cover 3 via upper and lower center disks 21 and 22. The diaphragm 20 is pushed down against the elastic force of the compression spring 25 by the signal pressure of the working fluid supplied from an external pressure source to the diaphragm chamber 24 through the supply port 23, and the valve head 10 is pushed down against the elastic force of the compression spring 25.
is seated on the valve seat 11. The valve box 2 is provided with an open hole 26 that opens the lower side of the diaphragm 20 to the atmosphere. Operated by differential pressure.
前記弁箱２の支持部１９先端には、ラビリンス
室２７が設けられており、該ラビリンス室２７内
に弁体９の弁頭１０が配置されている。このラビ
リンス室２７は、上記弁頭１０の反弁座当接面１
０ｂを密封的に覆うと共に、当該弁頭１０の外周
側面１０ｃと微小間隙ｇを有して対面するように
なつている。 A labyrinth chamber 27 is provided at the tip of the support portion 19 of the valve box 2, and the valve head 10 of the valve body 9 is disposed within the labyrinth chamber 27. This labyrinth chamber 27 is located at the abutting surface 1 of the valve head 10 opposite to the valve seat.
0b, and faces the outer circumferential side surface 10c of the valve head 10 with a minute gap g therebetween.
さらに、上記弁頭１０は、円柱状体よりなり、
その弁座当接面１０ａは外周側の平坦部１０a′と
その内周側の円錐部１０a″とから形成されてい
る。この弁頭１０が当接する弁座１１は、ゴム等
よりなる断面略コ字形の環状弾性体２８によつて
形成され、該弾性体２８は弁箱２に固着された弁
座形成部材２９の開口部３０に嵌着されている。
上記弾性体２８の上端内周には、環状のフイン３
１が内側に向けて一体的に突設されており、該フ
イン３１には平面コ字形状の切欠部３２が設けら
れている。また、上記弁座形成部材２９の開口部
３０の内径D1は、弁頭１０の外径D2より小さく
なつており、弾性体２８のフイン３１を除く内径
D3は、弁頭１０の平坦部１０a′の内径D4より大
きく設定されている。弾性体２８のフイン３１の
内径D5は、弁頭１０の平坦部１０a′の内径D4よ
り小さく設定されており、弁頭１０の平坦部１０
a′の一部及び円錐部１０a″がフイン３１に当接す
るものである。 Furthermore, the valve head 10 is made of a cylindrical body,
The valve seat abutting surface 10a is formed of a flat part 10a' on the outer circumferential side and a conical part 10a'' on the inner circumferential side. It is formed by a U-shaped annular elastic body 28, and the elastic body 28 is fitted into an opening 30 of a valve seat forming member 29 fixed to the valve box 2.
An annular fin 3 is provided on the inner periphery of the upper end of the elastic body 28.
1 integrally protrudes inward, and the fin 31 is provided with a notch 32 having a U-shape in plan. Furthermore, the inner diameter D 1 of the opening 30 of the valve seat forming member 29 is smaller than the outer diameter D 2 of the valve head 10 , and the inner diameter of the elastic body 28 excluding the fins 31 is smaller than the outer diameter D 2 of the valve head 10 .
D 3 is set larger than the inner diameter D 4 of the flat portion 10a' of the valve head 10. The inner diameter D5 of the fin 31 of the elastic body 28 is set smaller than the inner diameter D4 of the flat part 10a' of the valve head 10.
A portion of a' and the conical portion 10a'' come into contact with the fin 31.
以上の構成において、本考案に係る流量制御弁
は、次のように作動する。すなわち、ダイアフラ
ム室２４内に供給される作動流体の信号圧力によ
りダイアフラム２０を下降させると、弁頭１０が
押下げられて弁座１１に近づくため、第４図に示
すように、該弁頭１０の下降に伴なつてラビリン
ス室２７内に空間Ｓが徐々に形成される。このと
き、弁頭１０と弁座１１の間の間隔がせまくな
り、流入口５から流出口６へと流れる流体の流速
が速くなるので、弁頭１０の弁座当接面１０ａに
加わる圧力P2は減少する。一方、弁頭１０の上
流側に位置する流体が微小間隙ｇを介してラビリ
ンス室２７内に形成される空間Ｓ内に流入するた
め、弁頭１０の反弁座当接面１０ｂには、上流側
の流体がラビリンス効果を生じながら作用する。
従つて、弁頭１０の反弁座当接面１０ｂに加わる
圧力P3は、弁頭１０の上流側に位置する外部流
体の圧力P1より小さくなるため、弁頭１０の反
弁座当接面１０ｂに加わる圧力P3と弁座当接面
１０ａに加わる圧力P2との差を小さくすること
ができる。依つて、弁頭１０が弁座１１に近づい
た場合でも、弁頭１０の作動を安定させることが
できる。 In the above configuration, the flow control valve according to the present invention operates as follows. That is, when the diaphragm 20 is lowered by the signal pressure of the working fluid supplied into the diaphragm chamber 24, the valve head 10 is pushed down and approaches the valve seat 11. As shown in FIG. As the labyrinth chamber 27 descends, a space S is gradually formed within the labyrinth chamber 27. At this time, the distance between the valve head 10 and the valve seat 11 becomes narrower, and the flow rate of the fluid flowing from the inlet 5 to the outlet 6 becomes faster, so the pressure P applied to the valve seat contact surface 10a of the valve head 10 2 decreases. On the other hand, since the fluid located on the upstream side of the valve head 10 flows into the space S formed in the labyrinth chamber 27 through the minute gap g, the upstream The fluid on the side acts while creating a labyrinth effect.
Therefore, the pressure P3 applied to the anti-valve seat contact surface 10b of the valve head 10 is smaller than the pressure P1 of the external fluid located upstream of the valve head 10, so that the pressure P3 applied to the anti-valve seat abutment surface 10b of the valve head 10 The difference between the pressure P 3 applied to the surface 10b and the pressure P 2 applied to the valve seat contact surface 10a can be reduced. Therefore, even when the valve head 10 approaches the valve seat 11, the operation of the valve head 10 can be stabilized.
さらに、上記弁頭１０が弁座１１に近づくと、
第５図に示すように、弁座当接面１０ａの円錐部
１０a″が弁座１１を構成する弾性体２８のフイン
３１に接触し、流体はフイン３１に設けられた切
欠部３２によつて流量が制御される。この際、弁
頭１０は弾性体２８のフイン３１に弾性的に支持
されるので動きが安定する。前記ダイアフラム室
２４の圧力がさらに高くなると、弁頭１０が押下
げられ、弁座当接面１０ａの円錐部１０a′によつ
てフイン３１が変形する。このように、フイン３
１が変形すると、切欠部３２の開口面積が徐々に
減少していく。最後に、第６図に示すように、弁
座当接面１０ａの円錐部１０a″がフイン３１の切
欠部３２を完全に閉塞すると共に、該弁座当接面
１０ａの平坦部１０a′が弁座１１を構成する弾性
体２８の上端面２８′に当接して流量がゼロとな
る。しかして、弁頭１０が弁座１１に近づいて、
弁座当接面１０ａの円錐部１０a″が弁座１１を構
成する弾性体２８のフイン３１に接触した後は、
フイン３１の切欠部３２によつて流量が制御さ
れ、弁頭１０の下降に伴なつて切欠部３２の面積
が徐々に減少されるため、第７図に示すように、
信号圧力が大きくなつて流量が減少した場合に
も、空気等の流体の流量を滑らかに制御すること
ができる。 Furthermore, when the valve head 10 approaches the valve seat 11,
As shown in FIG. 5, the conical portion 10a'' of the valve seat contact surface 10a contacts the fins 31 of the elastic body 28 constituting the valve seat 11, and the fluid flows through the notches 32 provided in the fins 31. The flow rate is controlled.At this time, the valve head 10 is elastically supported by the fins 31 of the elastic body 28, so its movement is stabilized.When the pressure in the diaphragm chamber 24 further increases, the valve head 10 is pushed down. , the fin 31 is deformed by the conical portion 10a' of the valve seat contact surface 10a.
1 deforms, the opening area of the notch 32 gradually decreases. Finally, as shown in FIG. 6, the conical portion 10a'' of the valve seat contact surface 10a completely closes the notch 32 of the fin 31, and the flat portion 10a' of the valve seat contact surface 10a closes the valve seat contact surface 10a. The flow rate becomes zero as it comes into contact with the upper end surface 28' of the elastic body 28 that constitutes the seat 11.The valve head 10 approaches the valve seat 11,
After the conical portion 10a'' of the valve seat contact surface 10a comes into contact with the fins 31 of the elastic body 28 constituting the valve seat 11,
The flow rate is controlled by the notch 32 of the fin 31, and the area of the notch 32 gradually decreases as the valve head 10 descends, so as shown in FIG.
Even when the signal pressure increases and the flow rate decreases, the flow rate of fluid such as air can be smoothly controlled.
なお、図示の実施例では、フイン３１に切欠部
３２を１つ設けた場合について説明したが、これ
に限定されるわけではなく、フイン３１に切欠部
３２を複数設けても良く、この切欠部３２の形状
も平面Ｖ字形、半円形等任意の形状で良いことは
もちろんである。 In the illustrated embodiment, the fin 31 is provided with one notch 32, but the invention is not limited to this, and the fin 31 may be provided with a plurality of notches 32. Of course, the shape of 32 may be any shape such as a V-shape in plan or a semicircle.
また、図示の実施例では、流量制御弁がリード
弁１２を備えているものについて説明したが、こ
れに限定されるものではなく、絞り弁８の弁頭１
０に加わる圧力のアンバランスが問題となる他の
流量制御弁にも適用できることはもちろんであ
る。 Further, in the illustrated embodiment, the flow control valve has been described as having the reed valve 12, but the present invention is not limited to this, and the valve head 1 of the throttle valve 8
Of course, the present invention can also be applied to other flow rate control valves in which unbalance of pressure applied to zero is a problem.
もつとも、上記図示の実施例のように、絞り弁
８の下流側にリード弁１２を設けた場合には、弁
頭１０が閉弁しようとする際、該弁頭の弁座当接
面１０ａに加わる流体圧力が低下するが、このと
き、リード弁１２も閉弁状態に移行するので、こ
のリード弁１２の閉弁状態への移行によつて、上
記弁頭の弁座当接面１０ａに加わる流体圧力の低
下が緩和されるため、弁頭１０の不安定な閉弁が
より確実に防止できるといつた利点がある。 However, when the reed valve 12 is provided on the downstream side of the throttle valve 8 as in the embodiment shown above, when the valve head 10 is about to close, the valve seat abutment surface 10a of the valve head The applied fluid pressure decreases, but at this time, the reed valve 12 also shifts to the closed state, so that the fluid pressure is applied to the valve seat contact surface 10a of the valve head due to the shift of the reed valve 12 to the closed state. Since the drop in fluid pressure is alleviated, there is an advantage that unstable valve closing of the valve head 10 can be more reliably prevented.
（考案の効果）
本考案は以上の構成及び作用よりなるもので、
弁頭が弁座に近づいた場合、ラビリンス効果によ
つて流体の流量を滑らかに制御することができる
のはもちろんのこと、弁頭が弁座に非常に接近し
た場合でも、弁座を構成する弾性体のフインに切
欠部が設けられているため、当該切欠部の面積
を、弁頭の円錐形状に形成された弁座当接面によ
つて調節することにより、流体の流量を滑らかに
制御することができ、結果的に、すべての範囲に
わたつて空気等の流体の流量を滑らかに制御する
ことができる。(Effects of the invention) The invention consists of the above-mentioned configuration and operation.
When the valve head approaches the valve seat, it is possible to smoothly control the fluid flow rate due to the labyrinth effect. Since a notch is provided in the fin of the elastic body, the area of the notch can be adjusted by the conical valve seat contact surface of the valve head to smoothly control the fluid flow rate. As a result, the flow rate of fluid such as air can be smoothly controlled over the entire range.
第１図は本考案に係る流量制御弁の一実施例を
示す縦断面図、第２図は同流量制御弁の要部を示
す作動前の状態の縦断面図、第３図は第２図のＸ
方向矢視図、第４図は同流量制御弁の要部を示す
作動時の状態の縦断面図、第５図は同流量制御弁
の要部を示す第４図と異なつた作動時の状態の縦
断面図、第６図は同流量制御弁の要部を示す閉鎖
状態の縦断面図、第７図は同流量制御弁の動作を
示すグラフ、第８図は従来の流量制御弁を示す縦
断面図、第９図は同流量制御弁の要部を示す作動
状態の縦断面図、第１０図は同流量制御弁の作動
を示すグラフ、第１１図は従来の他の流量制御弁
を示す縦断面図、第１２図は同流量制御弁の要部
を示す作動状態の縦断面図、第１３図は同流量制
御弁の動作を示すグラフである。
符号の説明、２……弁箱、９……弁体、１０…
…弁頭、１０ａ……弁座当接面、１０ｂ……反弁
座当接面、１０ｃ……外周側面、１１……弁座、
２４……ダイアフラム室、２７……ラビリンス
室、２８……弾性体、３１……フイン、３２……
切欠部、ｇ……微小間隙。
FIG. 1 is a vertical cross-sectional view showing an embodiment of the flow control valve according to the present invention, FIG. 2 is a vertical cross-sectional view showing the main parts of the flow control valve in a state before operation, and FIG. X of
4 is a vertical sectional view of the main parts of the flow control valve in an operating state, and Fig. 5 is a different operating state from Fig. 4 showing the main parts of the flow control valve. 6 is a vertical sectional view showing the main parts of the flow control valve in a closed state, FIG. 7 is a graph showing the operation of the flow control valve, and FIG. 8 is a conventional flow control valve. 9 is a vertical sectional view showing the main parts of the same flow control valve in an operating state, FIG. 10 is a graph showing the operation of the same flow control valve, and FIG. 11 is a graph showing another conventional flow control valve. FIG. 12 is a vertical cross-sectional view showing essential parts of the flow control valve in an operating state, and FIG. 13 is a graph showing the operation of the flow control valve. Explanation of symbols, 2... Valve box, 9... Valve body, 10...
...Valve head, 10a... Valve seat contact surface, 10b... Opposite valve seat contact surface, 10c... Outer peripheral side, 11... Valve seat,
24...Diaphragm chamber, 27...Labyrinth chamber, 28...Elastic body, 31...Fin, 32...
Notch, g...micro gap.
Claims (1)
に配置され、ダイアフラム室に供給される作動流
体により前記弁座と協働して開閉弁する弁頭を備
えた弁体と、前記弁頭の反弁座当接面を密封的に
覆うと共に当該弁頭の外周側面と微小間隙を有し
て対面する前記弁箱側に支持されるラビリンス室
とを備えてなる流量制御弁において、前記弁頭の
弁座当接面を円錐形状に形成すると共に、前記弁
座を弾性体により形成し、前記弁座を構成する弾
性体の一部を内側に突出させて環状のフインを設
け、該フインに切欠部を設けたことを特徴とする
流量制御弁。 a valve seat provided in a valve box; a valve body disposed upstream of the valve seat and provided with a valve head that opens and closes the valve in cooperation with the valve seat by working fluid supplied to a diaphragm chamber; A flow control valve comprising: a labyrinth chamber that sealingly covers a contact surface of the valve head opposite to the valve seat and is supported on the valve box side facing the outer circumferential side surface of the valve head with a small gap therebetween; , the valve seat contacting surface of the valve head is formed into a conical shape, the valve seat is formed of an elastic body, and a part of the elastic body constituting the valve seat is made to protrude inward to provide annular fins. , A flow control valve characterized in that the fin is provided with a notch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16147484U JPH0117749Y2 (en) | 1984-10-25 | 1984-10-25 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP16147484U JPH0117749Y2 (en) | 1984-10-25 | 1984-10-25 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6175561U JPS6175561U (en) | 1986-05-21 |
| JPH0117749Y2 true JPH0117749Y2 (en) | 1989-05-23 |
Family
ID=30719382
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP16147484U Expired JPH0117749Y2 (en) | 1984-10-25 | 1984-10-25 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0117749Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007280819A (en) * | 2006-04-07 | 2007-10-25 | Aisan Ind Co Ltd | Flow control valve and fuel cell vehicle |
-
1984
- 1984-10-25 JP JP16147484U patent/JPH0117749Y2/ja not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6175561U (en) | 1986-05-21 |
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