JPS6362654B2 - - Google Patents
Info
- Publication number
- JPS6362654B2 JPS6362654B2 JP9788781A JP9788781A JPS6362654B2 JP S6362654 B2 JPS6362654 B2 JP S6362654B2 JP 9788781 A JP9788781 A JP 9788781A JP 9788781 A JP9788781 A JP 9788781A JP S6362654 B2 JPS6362654 B2 JP S6362654B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- control section
- pressure chamber
- diaphragm
- differential pressure
- 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
Links
- 238000002485 combustion reaction Methods 0.000 claims description 4
- 238000010586 diagram Methods 0.000 description 5
- 239000012530 fluid Substances 0.000 description 5
- 238000000034 method Methods 0.000 description 4
- 206010019233 Headaches Diseases 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23N—REGULATING OR CONTROLLING COMBUSTION
- F23N1/00—Regulating fuel supply
- F23N1/007—Regulating fuel supply using mechanical means
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Feeding And Controlling Fuel (AREA)
- Control Of Fluid Pressure (AREA)
- Regulation And Control Of Combustion (AREA)
Description
【発明の詳細な説明】
本発明は、ガスの圧力を制御する圧力制御装置
に関し、特に、ガスの圧力損失を小さくできると
ともに小さな力で駆動可能な圧力制御装置を提供
するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a pressure control device for controlling the pressure of gas, and in particular provides a pressure control device that can reduce pressure loss of gas and can be driven with small force.
一般にガス圧を制御する方法としては、弁体及
び弁座を設けるとともに前記弁体の上部にダイア
フラムを設けて構成される、衆知のガスガバナが
良く知られている。ところが、この種のガスガバ
ナは、ガス圧力を直接ダイアフラムに受けるた
め、動作させるためには、比較的大きな力を必要
とし、例えば、前記の力を発生する手段として、
電気的駆動部等を用いた場合、駆動部の大型化、
高コスト化を招いていた。上記問題点を解決する
手段として既に特願昭55−129705号（特開昭57−
54787号公報）として出願した差圧駆動方式の圧
力制御装置がある。第１図はその一実施例を示す
ものであり、図面とともに説明する。 Generally, as a method for controlling gas pressure, a well-known gas governor is constructed by providing a valve body and a valve seat, and also providing a diaphragm above the valve body. However, since this type of gas governor receives gas pressure directly on its diaphragm, it requires a relatively large force to operate.For example, as a means for generating the force,
When using an electric drive unit, etc., the drive unit becomes larger,
This led to higher costs. As a means to solve the above problems, Japanese Patent Application No. 55-129705
There is a pressure control device using a differential pressure drive method, which was filed as No. 54787. FIG. 1 shows one embodiment thereof, which will be explained with reference to the drawings.
第１図において１は流体入口、２は流体出口、
３は、流量に応じて径が決まる弁座である。４は
前記弁座３に対向して設けた弁体であり、その上
部にはダイアフラム５が、背圧室６と一次圧室７
を遮断するごとく設けられている。二次圧室８の
下流には、差圧を発生する差圧発生オリフイス９
が設けられており、さらに差圧発生オリフイス９
の下流側は、前記背圧室６と連通されている。 In FIG. 1, 1 is a fluid inlet, 2 is a fluid outlet,
3 is a valve seat whose diameter is determined according to the flow rate. 4 is a valve body provided opposite to the valve seat 3, and a diaphragm 5 is placed above the valve body, and a back pressure chamber 6 and a primary pressure chamber 7 are connected to each other.
It is set up so as to block the A differential pressure generating orifice 9 that generates a differential pressure is located downstream of the secondary pressure chamber 8.
In addition, a differential pressure generating orifice 9 is provided.
The downstream side of is in communication with the back pressure chamber 6.
１０は前記弁体４に力を伝達し、動作させるた
めの駆動部である。以上の構成において次に動作
原理を説明する。第１図において力の釣合いを考
えると、
Ｆ＋P1・SV＋P3・SD＝P1・SD＋P2・SV ……１
ここに、
Ｆ；駆動部の発生する力
P1；一次圧室圧力
P2；二次圧室圧力
P3；背圧室圧力
SV；弁体有効受圧面積
SD；ダイアフラム有効受圧面積
１式においてSDとSVを等しくすると、
Ｆ＝P2・SV−P3・SD＝SV（P2−P3） ……２
もしくは、
（P2−P3）＝Ｆ／SV ……３
となり、力Ｆに比例して差圧（P2−P3）、つまり
流量が制御されることがわかる。 Reference numeral 10 denotes a drive unit for transmitting force to the valve body 4 and operating it. Next, the principle of operation of the above configuration will be explained. Considering the balance of forces in Figure 1, F + P 1 · S V + P 3 · S D = P 1 · S D + P 2 · S V ... 1 Where, F; Force generated by the driving part P 1 ; Primary Pressure chamber pressure P 2 ; Secondary pressure chamber pressure P 3 ; Back pressure chamber pressure S V ; Valve body effective pressure receiving area S D ; Diaphragm effective pressure receiving area If S D and S V are equal in equation 1, then F=P 2・S V −P 3・S D = S V (P 2 − P 3 ) …2 or (P 2 − P 3 )=F/S V …3, and the differential pressure (P 2 −P 3 ), which means that the flow rate is controlled.
ここで、参考に差圧駆動方式でない場合、つま
り差圧発生オリフイス９がなく、しかも背圧室６
が大気に開放された形式の場合を同じように考え
てみると、
Ｆ＋P1・SV＝P1・SD＋P2・SV ……４
Ｆ＝P2・SV、SD＝SV ……５
もしくは、
P2＝Ｆ／SV ……６
となる。そこで力Ｆを比較すると、差圧駆動方式
では、P2とP3の差圧だけの力で動作させること
ができるのがわかる。 Here, for reference, if the differential pressure drive method is not used, that is, there is no differential pressure generating orifice 9, and the back pressure chamber 6
Similarly, if we consider the case where is open to the atmosphere, F+P 1・S V = P 1・S D +P 2・S V ……4 F=P 2・S V , S D =S V ...5 Or, P 2 = F/S V ...6. Comparing the forces F, it can be seen that with the differential pressure drive method, operation can be performed using only the force of the differential pressure between P 2 and P 3 .
以上説明したように第１図の構成は、小さな力
で動作させることができ、かつ、長期使用によ
り、万一ダイアフラム５が破損しても、大気中に
生ガスが流出しない極めて有効な手段である。 As explained above, the configuration shown in Fig. 1 can be operated with a small force, and is an extremely effective means of preventing raw gas from leaking into the atmosphere even if the diaphragm 5 is damaged after long-term use. be.
しかし、第１図構成は、差圧駆動方式にしたこ
とにより、以下に述べる問題点を有していた。 However, the configuration shown in FIG. 1 has the following problems due to the differential pressure drive system.
第１に、差圧発生オリフイス９を設けなければ
ならないため、その分だけ圧力損失が大きくな
り、使用できる器具バーナーの範囲が限定されて
しまうことである。すなわち、比較的低いバーナ
ーヘツド圧で、正常な燃焼をするバーナーしか使
用できない。 First, since the differential pressure generating orifice 9 must be provided, the pressure loss increases accordingly, and the range of appliance burners that can be used is limited. That is, only burners that produce normal combustion at relatively low burner head pressures can be used.
第２図は、弁開度と出口側圧力（バーナーヘツ
ド圧）の関係を示し、実線が差圧駆動方式の場合
を示す。差圧駆動方式の場合、同一弁開度L1に
対して、Pa−Pbだけ、すなわち、差圧発生オリ
フイス９の圧力損失分だけ出口側圧力が低くなる
ことがわかる。 FIG. 2 shows the relationship between the valve opening degree and the outlet side pressure (burner head pressure), and the solid line shows the case of the differential pressure drive system. In the case of the differential pressure drive system, it can be seen that the outlet side pressure is lowered by Pa-Pb, that is, by the pressure loss of the differential pressure generating orifice 9, for the same valve opening L1 .
第２の問題点は、供給圧P1の変動に対する出
口側圧力P3の変動、すなわち衆知のガバナ特性
を考えた場合、弁体４、及びダイアフラム５の有
効受圧面積のバラツキが大きく影響をおよぼし、
そのバラツキを吸収しようとする場合、前記差圧
発生オリフイス９部での圧力損失をさらに大きく
する必要があることである。以下、その点につい
て説明する。前記１式において、
P3＝Ｃ・P2 ……７
（Ｃ＜１）
SD＝ｋ・SV ……８
（ｋ≒１）
ただし
Ｃ；圧力損失係数
ｋ；面積係数
１式に７、８式を代入すると、
Ｆ＋P1・SV＋Ｃ・P2・ｋ・SV＝P1・ｋ・SV
＋P2・SV ……９
９式を変形すると、
Ｆ＋P1・SV（１−ｋ）＝P2・SV（１−Ｃ・ｋ）
∴P2＝Ｆ＋P1・SV（１−ｋ）／SV（１−Ｃ・ｋ）
＝Ｆ／SV・（１−Ｃ・ｋ）＋１−ｋ／１−Ｃ・ｋ・
P1
……10
また、
P3＝Ｃ・P2＝Ｃ・Ｆ／SV（１−Ｃ・ｋ）＋１−ｋ／１−
Ｃ・ｋ・
Ｃ・P1 ……11
11式より供給圧P1の変動ΔP1に対する出口側圧
力P3の変動ΔP3の比ηつまりガバナ特性は12式に
よつてあらわされる。 The second problem is that when considering the variation of the outlet side pressure P 3 with respect to the variation of the supply pressure P 1 , that is, the well-known governor characteristics, the variation in the effective pressure receiving area of the valve body 4 and the diaphragm 5 has a large influence. ,
In order to absorb this variation, it is necessary to further increase the pressure loss at the differential pressure generating orifice 9 section. This point will be explained below. In the above equation 1, P 3 = C・P 2 ... 7 (C<1) S D = k・S V ... 8 (k≒1) where C: pressure loss coefficient k; area coefficient 7, Substituting equation 8, F+P 1・S V +C・P 2・k・S V =P 1・k・S V +P 2・S V ……9 Transforming equation 9, we get F+P 1・S V (1− k)=P 2・S V (1-C・k) ∴P 2 =F+P 1・S V (1-k)/S V (1-C・k) =F/S V・(1-C・k)+1-k/1-C・k・
P 1 ...10 Also, P 3 =C・P 2 =C・F/S V (1−C・k)+1−k/1−
C・k・C・P 1 ...11 From Equation 11, the ratio η of the variation ΔP 3 in the outlet side pressure P 3 to the variation ΔP 1 in the supply pressure P 1 , that is, the governor characteristic, is expressed by Equation 12.
η＝ΔP3／ΔP1＝１−ｋ／１−Ｃ・ｋ・Ｃ＝１−ｋ／１
／Ｃ−ｋ……12
第３図は、差圧発生オリフイス９部での圧力損
失係数Ｃをパラメータとした場合の面積係数ｋと
圧力変動比ηを12式によりもとめたものである。
変動比ηを小さくしたい場合、つまり供給圧P1
の変動に対して、出口側圧力P3を一定に保ちた
い場合、面積係数ｋは１に近づける必要があるこ
と、及び圧力損失係数Ｃの値が小さいほど、つま
り差圧発生オリフイス９での圧力損失を大きくす
るほど、変動比ηは小さくなるのがわかる。η=ΔP 3 /ΔP 1 =1−k/1−C・k・C=1−k/1
/C-k...12 FIG. 3 shows the area coefficient k and pressure fluctuation ratio η obtained using equation 12 when the pressure loss coefficient C at the differential pressure generating orifice 9 is used as a parameter.
If you want to reduce the fluctuation ratio η, that is, supply pressure P 1
If you want to keep the outlet side pressure P 3 constant against fluctuations in It can be seen that the larger the loss, the smaller the fluctuation ratio η.
ところで、実用上、製造、組立段階での各寸法
精度のバラツキ、及びダイアフラム５の弁開度に
よる、有効受圧面積の変化等を考えた場合、面積
係数ｋを１にすることは、ほとんど不可能であ
り、したがつて圧力損失係数Ｃの値をできるだけ
小さくして、すなわち差圧発生オリフイス９での
圧力損失を大きくして、そのバラツキを吸収しな
くてはならない。 However, in practice, it is almost impossible to set the area coefficient k to 1 when considering variations in dimensional accuracy at the manufacturing and assembly stages and changes in the effective pressure-receiving area due to the valve opening of the diaphragm 5. Therefore, the value of the pressure loss coefficient C must be made as small as possible, that is, the pressure loss at the differential pressure generating orifice 9 must be increased to absorb this variation.
本発明は上記従来の問題点を解消するものであ
り、差圧駆動方式の圧力制御装置において圧力損
失が小さく、且つ良好なガバナ特性が得られると
ともに、更に小さな力で駆動できる圧力制御装置
を提供することを目的とする。 The present invention solves the above-mentioned conventional problems, and provides a pressure control device that has low pressure loss and good governor characteristics in a differential pressure drive type pressure control device, and can be driven with even smaller force. The purpose is to
この目的を達成するために本発明は第１弁体、
第１弁座及び第１ダイアフラムから構成される第
１制御部と、前記第１制御部よりも小口径の第２
弁体、第２弁座及び第２ダイアフラムから構成さ
れる第２制御部を有し、前記第１制御部の一次圧
室イと第２制御部の一次圧室ロを連通し、且つ前
記第１制御部の背圧室ハと第２制御部の二次圧室
ニを連通するとともに、前記第２制御部の二次圧
室ニの下流側に差圧発生部を設け、その差圧発生
部の下流側と第２制御部の背圧室ホを連通し、且
つ前記差圧発生部の下流側を導管によつて大気側
に連通する構成としたものである。 In order to achieve this object, the present invention provides a first valve body,
a first control section consisting of a first valve seat and a first diaphragm; and a second control section having a smaller diameter than the first control section.
The second control section includes a valve body, a second valve seat, and a second diaphragm, and communicates the primary pressure chamber A of the first control section with the primary pressure chamber B of the second control section. The back pressure chamber C of the first control section communicates with the secondary pressure chamber D of the second control section, and a differential pressure generating section is provided downstream of the secondary pressure chamber D of the second control section, and the differential pressure is generated. The downstream side of the differential pressure generating section is communicated with the back pressure chamber E of the second control section, and the downstream side of the differential pressure generating section is communicated with the atmosphere through a conduit.
この構成により第２制御部に差圧発生部を設け
て充分な圧力損失係数Ｃを確保できるためガバナ
特性を良好にできるとともに第１制御部に差圧発
生部がないため圧力損失が低減できる。また第２
制御部の口径は第１制御部よりも小さいため圧力
制御に要する駆動力を更に小さくできる。以下本
発明の実施例を図面とともに説明する。 With this configuration, a differential pressure generating section is provided in the second control section, and a sufficient pressure loss coefficient C can be ensured, so that governor characteristics can be improved, and since there is no differential pressure generating section in the first control section, pressure loss can be reduced. Also the second
Since the diameter of the control section is smaller than that of the first control section, the driving force required for pressure control can be further reduced. Embodiments of the present invention will be described below with reference to the drawings.
第４図は、本発明の一実施例を示し、１１は流
体入口、１２は流体出口であり、その下流には器
具ノズル１３が設けられ、バーナー１４で燃焼す
る。１５は第１弁座であり、１６は第１弁座１５
に対向して設けた、第１弁体である。１７は第１
弁体１６の上部に設けた第１ダイアフラムであ
り、以上で第１制御部１８を構成する。１９は、
少なくとも第１弁座１５よりも径が小さい第２弁
座であり、２０は第２弁座１９に対向して設けた
第２弁体、２１は第２弁体２０に上部に設けた第
２ダイアフラムである。以上で第２制御部２２を
構成する。そして第１制御部１８の一次圧室イと
第１制御部２２の一次圧室ロとを第１導通路２３
で連通し、且つ、第１制御部１８の背圧室ハと第
２制御部２２の二次圧室ニを絞り２４を介して連
通する。さらに、第２制御部２２の二次圧室ニの
下流には、差圧発生オリフイス２５を設け、その
下流側を第２導通路２６で背圧室ホと連通すると
ともに導管２７で大気側であるバーナー１４の近
傍へ着火可能に導く。２８は、第２弁体２０に作
用して動作させる力Ｆを発生する駆動部である。 FIG. 4 shows an embodiment of the present invention, in which 11 is a fluid inlet, 12 is a fluid outlet, downstream of which is provided an instrument nozzle 13 for combustion in a burner 14. 15 is the first valve seat, 16 is the first valve seat 15
The first valve body is provided opposite to the first valve body. 17 is the first
This is a first diaphragm provided on the upper part of the valve body 16, and the above constitutes the first control section 18. 19 is
A second valve seat having a diameter smaller than at least the first valve seat 15, 20 is a second valve body provided opposite to the second valve seat 19, and 21 is a second valve seat provided above the second valve seat 20. It is a diaphragm. The second control section 22 is configured above. The primary pressure chamber A of the first control section 18 and the primary pressure chamber B of the first control section 22 are connected to the first conduction path 23.
Also, the back pressure chamber C of the first control section 18 and the secondary pressure chamber D of the second control section 22 are communicated via the throttle 24. Furthermore, a differential pressure generating orifice 25 is provided downstream of the secondary pressure chamber 2 of the second control section 22, and its downstream side is communicated with the back pressure chamber 2 through a second conduit 26, and connected to the atmosphere side through a conduit 27. It is led to the vicinity of a certain burner 14 so that it can be ignited. 28 is a drive unit that generates a force F that acts on the second valve body 20 to operate it.
以上の構成において動作を説明する。 The operation in the above configuration will be explained.
まず、第２制御部２２の力の釣合いを考える
と、
Ｆ＋P1・SV2＋P3・SD2＝P1・SD2＋P′2・SV2
……13
ここに、
Ｆ；駆動部の発生する力
P1；一次圧室イ，ロの圧力
P′2；二次圧室ニの圧力
P3；背圧室ホの圧力
SV2；第２弁体２０の有効受圧面積
SD2；第２ダイアフラム２１の有効受圧面積
13式においてSV2とSD2を等しくすると、
Ｆ＝P′2・SV2−P3・SD2＝SV2（P′2−P3） ……14
または、
P′2−P3＝Ｆ／SV2 ……15
となり力Ｆに比例して圧力P′2及びP3が制御され
るのがわかる。 First, considering the balance of forces in the second control section 22, F+P 1・S V2 +P 3・S D2 =P 1・S D2 +P′ 2・S V2
...13 Here, F; Force generated by the drive unit P 1 ; Pressure P' 2 in primary pressure chambers A and B; Pressure P 3 in secondary pressure chamber D; Pressure S V2 in back pressure chamber E; Effective pressure-receiving area S D2 of the valve body 20 ; Effective pressure-receiving area of the second diaphragm 21 If S V2 and S D2 are equal in equation 13, then F = P' 2・S V2 −P 3・S D2 = S V2 (P' 2 −P 3 ) ...14 Or, P′ 2 −P 3 =F/S V2 ...15 It can be seen that the pressures P′ 2 and P 3 are controlled in proportion to the force F.
次に第１制御部１８も同様に考えると、
P1・SD1＋P2・SV1＝P′2・SD1＋P1・SV1 ……16
ここに、
P2；二次圧室への圧力
SV1；第１弁体１６の有効受圧面積
SD1；第１ダイアフラム１７の有効受圧面積
16式でSV1とSD1を等しくすると、
P2・SV1＝P′2・SD1 ∴P2＝P′2 ……17
となり、力Ｆに比例して二次圧室への圧力P2を
制御できるのがわかる。 Next, considering the first control section 18 in the same way, P 1 · S D1 + P 2 · S V1 = P' 2 · S D1 + P 1 · S V1 ...16 Here, P 2 ; Pressure S V1 ; Effective pressure receiving area of the first valve body 16 S D1 ; Effective pressure receiving area of the first diaphragm 17 If S V1 and S D1 are equal in equation 16, then P 2・S V1 = P′ 2・S D1 ∴P 2 = P' 2 ...17, and it can be seen that the pressure P 2 to the secondary pressure chamber can be controlled in proportion to the force F.
ここで14式に示すように、二次圧室への圧力を
制御するのに要する力Ｆは、第１制御部１８の大
きさにかかわらず、第２制御部２２の第２弁体２
０もしくは、第２ダイアフラム２１の有効受圧面
積と、差圧発生オリフイス２５の圧力損失の大き
さによつてきまり、すなわち第１制御部１８の口
径よりも第２制御部２２の口径を小さくすること
により第１図に示す従来例よりもさらに小さな力
Ｆで大流量を制御することができる。 Here, as shown in equation 14, the force F required to control the pressure to the secondary pressure chamber is determined by the force F required for the second valve body 2 of the second control section 22, regardless of the size of the first control section 18.
0 or depending on the effective pressure receiving area of the second diaphragm 21 and the magnitude of pressure loss of the differential pressure generating orifice 25, that is, the diameter of the second control section 22 should be smaller than the diameter of the first control section 18. Accordingly, a large flow rate can be controlled with an even smaller force F than in the conventional example shown in FIG.
また、流体出口１２側には差圧発生オリフイス
２５がないため、圧力損失も小さくなる。 Furthermore, since there is no differential pressure generating orifice 25 on the fluid outlet 12 side, pressure loss is also reduced.
さらに、本発明では、差圧発生オリフイス２５
の下流側をバーナー１４の近傍へ導き着火させる
構造のため、差圧発生オリフイス２５での圧力損
失P′2−P3を小さくできる。したがつて前記圧力
損失係数Ｃの値を小さくでき、面積係数ｋのバラ
ツキによる変動比η1の値を小さくすることが容易
となる。なお本発明の実施例における変動比η1
は、P1の変動ΔP1に対するP2の変動ΔP2の比であ
り、10式から
η1＝ΔP2／ΔP1＝ΔP′2／ΔP1＝１−ｋ／１−Ｃ・ｋ
……18
となり、12式及び第３図に示したものと若干異な
り第５図のようになるが、同様の特性となる。 Furthermore, in the present invention, the differential pressure generating orifice 25
Because of the structure in which the downstream side of the burner is guided to the vicinity of the burner 14 and ignited, the pressure loss P' 2 -P 3 at the differential pressure generating orifice 25 can be reduced. Therefore, the value of the pressure loss coefficient C can be reduced, and the value of the fluctuation ratio η 1 due to variation in the area coefficient k can be easily reduced. Note that the variation ratio η 1 in the embodiment of the present invention
is the ratio of the variation ΔP 2 in P 2 to the variation ΔP 1 in P 1, and from equation 10, η 1 = ΔP 2 /ΔP 1 = ΔP′ 2 /ΔP 1 = 1−k/1−C・k
...18, which is slightly different from that shown in Equation 12 and Fig. 3, as shown in Fig. 5, but with similar characteristics.
また長期の使用により、第１ダイアフラム１
７、第２ダイアフラム２１が破損した場合でも、
生ガスは大気中に洩れることなく、導管２７の開
孔部で着火し、安全である。 Also, due to long-term use, the first diaphragm 1
7. Even if the second diaphragm 21 is damaged,
The raw gas is ignited at the opening of the conduit 27 without leaking into the atmosphere, and is therefore safe.
以上詳細に説明したように本発明は、第１制御
部と第２制御部を設けて、それらの室を関連さ
せ、第２制御部を差圧駆動方式とするとともに、
その出口側を燃焼熱源近傍に導き着火させるよう
にしたものであり、
１ 極めて小さな力で大流量の制御が可能とな
り、駆動部のコンパクト化、低コスト化を実現
する。 As described in detail above, the present invention provides a first control section and a second control section, associates these chambers, and makes the second control section a differential pressure drive system.
The outlet side is guided to the vicinity of the combustion heat source for ignition. 1. It is possible to control a large flow rate with extremely small force, making the drive unit more compact and lower in cost.
２ 差圧駆動方式にもかかわらず、圧力損失が小
さく、且つダイアフラム、弁体の有効受圧面積
のバラツキに起因するガバナ特性のバラツキを
小さくすることができる。2. Despite the differential pressure drive system, the pressure loss is small, and variations in governor characteristics caused by variations in the effective pressure-receiving areas of the diaphragm and valve body can be reduced.
３ ダイアフラムが万一破損しても、生ガスが大
気中へ流出せず、安全である。3. Even if the diaphragm were to break, raw gas would not leak into the atmosphere, making it safe.
などの重要な効果を有する圧力制御装置を提供す
るものである。The present invention provides a pressure control device that has the following important effects.
なお駆動部としてどのような型式のものを使用
しても、同様の効果を奏する。 Note that the same effect can be achieved no matter what type of drive unit is used.
第１図は本発明の従来例を示す圧力制御装置の
構造図、第２図は弁開度と出口側圧力の関係を示
す特性図、第３図は従来例における圧力損失係数
をパラメータとした場合の面積係数と圧力変動比
の関係を示す特性図、第４図は本発明の一実施例
を示す圧力制御装置の構造図、第５図は本発明に
おける圧力損失係数をパラメータとした場合の面
積係数と圧力変動比の関係を示す特性図である。
１４……バーナー、１５……第１弁座、１６…
…第１弁体、１７……第１ダイアフラム、第１制
御部、１９……第２弁座、２０……第２弁体、２
１……第２ダイアフラム、２２……第２制御部、
２５……差圧発生オリフイス、２７……導管、２
８……駆動部、イ，ロ……一次圧室、ハ，ホ……
背圧室、ニ，ヘ……二次圧室。
Figure 1 is a structural diagram of a pressure control device showing a conventional example of the present invention, Figure 2 is a characteristic diagram showing the relationship between valve opening and outlet side pressure, and Figure 3 is a conventional example with pressure loss coefficient as a parameter. Fig. 4 is a structural diagram of a pressure control device showing an embodiment of the present invention, and Fig. 5 is a characteristic diagram showing the relationship between the area coefficient and pressure fluctuation ratio in the case of the present invention. FIG. 3 is a characteristic diagram showing the relationship between area coefficient and pressure fluctuation ratio. 14... Burner, 15... First valve seat, 16...
...first valve body, 17...first diaphragm, first control section, 19...second valve seat, 20...second valve body, 2
1... second diaphragm, 22... second control section,
25... Differential pressure generating orifice, 27... Conduit, 2
8... Drive unit, a, b... primary pressure chamber, c, ho...
Back pressure chamber, d, f... secondary pressure chamber.
Claims (1)
ら構成される第１制御部と、前記第１制御部より
も小口径の第２弁体と第２弁座及び第２ダイアフ
ラムより構成される第２制御部と、前記第２制御
部を動作させる駆動部を有し、前記第１制御部の
一次圧室イと第２制御部の一次圧室ロを連通し、
且つ前記第１制御部の背圧室ハと第２制御部の二
次圧室ニを連通するとともに前記第２制御部の二
次圧室ニの下流に差圧発生部を設け、その差圧発
生部の下流側と第２制御部の背圧室ホを連通し、
且つ前記差圧発生部の下流側を大気側に連通する
導管を設けた圧力制御装置。 ２ 導管の開口端を燃焼熱源近傍に配設した特許
請求の範囲第１項記載の圧力制御装置。[Scope of Claims] 1. A first control section composed of a first valve body, a first valve seat, and a first diaphragm, a second valve body having a smaller diameter than the first control section, a second valve seat, and It has a second control section composed of a second diaphragm, and a drive section that operates the second control section, and communicates the primary pressure chamber A of the first control section with the primary pressure chamber B of the second control section. ,
The back pressure chamber C of the first control section communicates with the secondary pressure chamber D of the second control section, and a differential pressure generating section is provided downstream of the secondary pressure chamber D of the second control section, and the differential pressure is The downstream side of the generation part and the back pressure chamber E of the second control part are communicated,
A pressure control device further includes a conduit that communicates the downstream side of the differential pressure generating section with the atmosphere. 2. The pressure control device according to claim 1, wherein the open end of the conduit is disposed near the combustion heat source.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9788781A JPS5815A (en) | 1981-06-24 | 1981-06-24 | Pressure control device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9788781A JPS5815A (en) | 1981-06-24 | 1981-06-24 | Pressure control device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5815A JPS5815A (en) | 1983-01-05 |
| JPS6362654B2 true JPS6362654B2 (en) | 1988-12-05 |
Family
ID=14204255
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9788781A Granted JPS5815A (en) | 1981-06-24 | 1981-06-24 | Pressure control device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5815A (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4904805B2 (en) * | 2004-12-27 | 2012-03-28 | 住友化学株式会社 | Polymer compound and polymer light emitting device using the same |
| JP5547608B2 (en) * | 2010-11-04 | 2014-07-16 | 東京瓦斯株式会社 | Pressure regulator |
-
1981
- 1981-06-24 JP JP9788781A patent/JPS5815A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5815A (en) | 1983-01-05 |
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