JPS6154130B2 - - Google Patents

Info

Publication number
JPS6154130B2
JPS6154130B2 JP56131148A JP13114881A JPS6154130B2 JP S6154130 B2 JPS6154130 B2 JP S6154130B2 JP 56131148 A JP56131148 A JP 56131148A JP 13114881 A JP13114881 A JP 13114881A JP S6154130 B2 JPS6154130 B2 JP S6154130B2
Authority
JP
Japan
Prior art keywords
valve
pressure chamber
valve body
flow rate
burner
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
Application number
JP56131148A
Other languages
Japanese (ja)
Other versions
JPS5833024A (en
Inventor
Takashi Tanahashi
Shigeru Shirai
Masaji Yamauchi
Tomohide Matsumoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Electric Industrial Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Matsushita Electric Industrial Co Ltd filed Critical Matsushita Electric Industrial Co Ltd
Priority to JP56131148A priority Critical patent/JPS5833024A/en
Publication of JPS5833024A publication Critical patent/JPS5833024A/en
Publication of JPS6154130B2 publication Critical patent/JPS6154130B2/ja
Granted legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N1/00—Regulating fuel supply
    • F23N1/005—Regulating fuel supply using electrical or electromechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/14—Fuel valves electromagnetically operated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/12—Fuel valves
    • F23N2235/20—Membrane valves

Description

【発明の詳細な説明】 本発明はガス燃焼機器において小能力時と大能
力時にバーナを自動的に切換えてさらに比例制御
する能力制御手段に関し、バーナ切換時に一時的
にガス供給量が変化するのを防止する装置に関す
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a capacity control means for automatically switching the burner between small capacity and high capacity in gas combustion equipment and further proportionally controlling the gas supply amount when the burner is switched. The present invention relates to a device for preventing.

第１図は本発明、従来例共通のガス湯沸器の場
合のシステム図である。ガスＱは矢印の方向に流
れ元電磁弁Vo、比例制御弁PV、を経て分岐管PY
に至り、二経路に分れてそれぞれ第１バーナ
B1、第２バーナB2に電磁弁V1，V2を経て供給さ
れる。熱交換器HEには水Ｗが矢印の方向に流
れ、熱交換器出口付近に温度検出器Tnが設けら
れ、出湯温度を検出し、電気制御部Ｃに入力さ
れ、信号処理し、比例制御弁PV、電磁弁V0，
V1，V2に動作信号を出力する。そして出湯温度
が一定になるよう負荷に応じて比例制御弁PV、
電磁弁V1を制御し、電磁弁V1，V2共OFF時はバ
ーナの燃焼が停止する。 FIG. 1 is a system diagram of a gas water heater common to the present invention and a conventional example. Gas Q flows in the direction of the arrow through the source solenoid valve Vo, proportional control valve PV, and then to the branch pipe PY.
is reached, and is divided into two routes, each of which goes to the first burner.
B 1 is supplied to the second burner B 2 via solenoid valves V 1 and V 2 . Water W flows in the direction of the arrow in the heat exchanger HE, and a temperature detector Tn is provided near the outlet of the heat exchanger to detect the outlet hot water temperature, input it to the electric control unit C, process the signal, and operate the proportional control valve. PV, solenoid valve V 0 ,
Outputs operating signals to V 1 and V 2 . Then, the proportional control valve PV is operated according to the load so that the hot water temperature remains constant.
Controls the solenoid valve V1 , and when both the solenoid valves V1 and V2 are OFF, combustion of the burner stops.

ここでバーナを２分割する理由は周知の通り、
バーナの最大燃焼量に対しガスの供給量を制御弁
により少くしてゆくとやがてバツクフアイヤーを
するなどバーナの燃焼巾に限界があるので、小能
力時には一方のバーナを燃焼停止し機器としての
燃焼巾を拡大しようとするものである。 As is well known, the reason for dividing the burner into two parts is as follows.
If the gas supply amount is reduced by the control valve to the maximum combustion amount of the burner, there will be a limit to the combustion width of the burner, such as a backfire occurring. It is an attempt to expand the

ここで従来例では比例制御弁PVに第２図に示
す圧力制御型比例制御弁が用いられていた。 Here, in the conventional example, a pressure control type proportional control valve shown in FIG. 2 was used as the proportional control valve PV.

第２図はおいて１は流体の入口、２は出口、３
は弁座、４は弁体でダイヤフラム５の中央部に固
着されている。コイル６軸心にはプランジヤ７が
板ばね８により、無摺動で上下動自在に支持され
ている。前記プランジヤ７の下端部はダイヤフラ
ム５の中央部に当接し、弁体４に力が作用するよ
うになつている。 In Figure 2, 1 is the fluid inlet, 2 is the outlet, and 3
4 is a valve seat, and 4 is a valve body that is fixed to the center of the diaphragm 5. A plunger 7 is supported on the axis of the coil 6 by a plate spring 8 so as to be able to move up and down without sliding. The lower end of the plunger 7 abuts against the center of the diaphragm 5, so that a force acts on the valve body 4.

上記構成において弁体４の上流側の一次圧室９
の圧力をP1、弁体４の下流側の二次圧室１０の圧
力をP2、弁体４の受圧面積をＳV、ダイヤフラム
５の受圧面積をＳDとし、コイル６とプランジヤ
７などからなる駆動部によつて弁体４に作用する
力をＦとすると P2＝Ｆ＋Ｐ１・ＳＶ−Ｐ１・ＳＤ／ＳＶ ここでＳVとＳDはほゞ等しくなるようにしてあ
るのでP2≒Ｆ／ＳＶとなる。したがつて二次圧P2は電 磁駆動部の発生する力Ｆに応じて可変できる。つ
まりコイル６に流す電流を制御することにより二
次圧P2を制御できる。 In the above configuration, the primary pressure chamber 9 on the upstream side of the valve body 4
P 1 is the pressure in the secondary pressure chamber 10 on the downstream side of the valve body 4, P 2 is the pressure in the secondary pressure chamber 10 on the downstream side of the valve body 4, S V is the pressure receiving area of the valve body 4, S D is the pressure receiving area of the diaphragm 5, and the coil 6, plunger 7, etc. Letting F be the force acting on the valve body 4 by the drive unit consisting of Therefore, P 2 ≒F/ SV . Therefore, the secondary pressure P2 can be varied according to the force F generated by the electromagnetic drive section. That is, by controlling the current flowing through the coil 6, the secondary pressure P2 can be controlled.

つまり従来例第２図の圧力型比例制御弁ではガ
スの流量や一次圧に関係なく弁体４に作用する力
Ｆによつて二次圧P2が制御される。 In other words, in the conventional pressure type proportional control valve shown in FIG. 2, the secondary pressure P2 is controlled by the force F acting on the valve body 4, regardless of the gas flow rate or the primary pressure.

次に第２図の圧力型比例制御弁を第１図の湯沸
器に用いた従来例の動作を第３図の従来例特性図
により説明する。ここで簡単の為に第１バーナ
B1と第２バーナB2は同一とする。 Next, the operation of a conventional example in which the pressure type proportional control valve shown in FIG. 2 is used in the water heater shown in FIG. 1 will be explained with reference to the characteristic diagram of the conventional example shown in FIG. Here, for simplicity, the first burner
It is assumed that B 1 and the second burner B 2 are the same.

今バーナ全体の燃焼量をＱとしバーナB1，B2
のそれぞれの燃焼量をｇとすると、湯沸器の負荷
が大きく比例弁のコイル電流ｉ（以下比例弁電流
という）が最大電流i1でバーナB1，B2がそれぞれ
最大燃焼量ですなわちバーナ全体の燃焼量Ｑ＝
Q1で燃焼している状態から比例電流ｉを下げて
来ると曲線ａを経て、ｉ＝i3でＱ＝Q2となる。さ
らに湯沸器の負荷が小さくなると電磁弁V1が閉
じられるがこの瞬間前述のように圧力制御型比例
制御弁では二次圧P2が一定である。かつバーナ全
体の燃焼量ＱはQ2からQ3に1/2となる。つまりこ
の点で不連続に湯沸器のバーナ燃焼量が変化して
しまい、第１図で説明した出湯温度が下がりすぎ
る。そして出湯温度検出器Tnがそれを検出し比
例弁電流ｉをi2まで増大しＱ＝Q2とする。そして
さらに負荷が小さくなるとバーナB2のみが燃焼
しその燃焼量を比例制御弁が小さくしｉ＝i3でＱ
＝Q3とする。 Now let the combustion amount of the entire burner be Q, and burners B 1 , B 2
If the combustion amount of each of is g, then the load on the water heater is large and the coil current i of the proportional valve (hereinafter referred to as proportional valve current) is the maximum current i 1 and burners B 1 and B 2 are at their maximum combustion amount, that is, the burner Total combustion amount Q=
When the proportional current i is lowered from the combustion state at Q 1 , it passes through curve a and becomes Q=Q 2 at i=i 3 . Furthermore, when the load on the water heater becomes smaller, the solenoid valve V 1 is closed, but at this moment, the secondary pressure P 2 is constant in the pressure-controlled proportional control valve as described above. Moreover, the combustion amount Q of the entire burner becomes 1/2 from Q 2 to Q 3 . In other words, at this point, the burner combustion amount of the water heater changes discontinuously, and the hot water temperature described in FIG. 1 drops too much. Then, the outlet hot water temperature sensor Tn detects this and increases the proportional valve current i to i 2 so that Q=Q 2 . When the load further decreases, only burner B 2 burns, and the proportional control valve reduces the amount of combustion, so that i = i 3 and Q
= Q 3 .

逆に負荷が増加する時も、電磁弁V1が閉じた
まゝ負荷の増加に応じて比例弁電流が増加しｉ＝
i2でＱ＝Q2となり電磁弁V1が開いてＱ＝Q4とな
り出湯温度が上がりすぎてそれを温度検出器Tn
が検出し、電気制御弁Ｃにより比例弁電流ｉを減
少しｉ＝i3とし、Ｑ＝Q3としバーナB1，B2が小さ
い炎で燃焼し、さらに負荷の増大に応じて比例弁
電流が増加しｉ＝i1で最大能力Ｑ＝Q1となる。 Conversely, even when the load increases, the solenoid valve V 1 remains closed and the proportional valve current increases in accordance with the increase in load, i=
At i 2 , Q = Q 2 , solenoid valve V 1 opens, Q = Q 4 , and the temperature of the hot water rises too much, which is detected by the temperature detector Tn.
is detected, the electric control valve C reduces the proportional valve current i to make i = i 3 , Q = Q 3 , and burners B 1 and B 2 burn with small flames, and then the proportional valve current decreases as the load increases. increases, and when i=i 1 , the maximum capacity becomes Q=Q 1 .

勿論湯沸器の実使用時は燃焼量Q2をはさんで
絶えず増減するので従来からこの不連続な制御を
改善することが重要な課題であつた。 Of course, when a water heater is actually used, the combustion amount Q2 constantly increases and decreases, so improving this discontinuous control has traditionally been an important issue.

本発明は上記従来例の不連続な制御を連続にす
るものである。 The present invention makes the discontinuous control of the conventional example continuous.

第４図に本発明に用いる流量制御型比例制御弁
の一実施例を示す。 FIG. 4 shows an embodiment of a flow rate control type proportional control valve used in the present invention.

第４図において１は流体の入口、２は出口、３
は弁座、４は弁体でダイヤフラム５の中央部に固
着されている。コイル６の軸心にはプランジヤ７
が板ばね８により、無摺動で上下動自在なように
支持されている。前記プランジヤ７の下端部はダ
イヤフラム５の中央部に当接し、弁体４に力が作
用するようになつている。弁体４の上流側を一次
圧室９、下流側を二次圧室１０とし二次圧室１０
のさらに下流側にオリフイスによる絞り部１３を
設け、低圧部１４を形成し、前記低圧部１４と背
圧室１１との間に連通路１５を設け連通させた構
成である。 In Fig. 4, 1 is the inlet of the fluid, 2 is the outlet, and 3
4 is a valve seat, and 4 is a valve body that is fixed to the center of the diaphragm 5. A plunger 7 is located at the axis of the coil 6.
is supported by a leaf spring 8 so that it can move vertically without sliding. The lower end of the plunger 7 abuts against the center of the diaphragm 5, so that a force acts on the valve body 4. The upstream side of the valve body 4 is a primary pressure chamber 9, and the downstream side is a secondary pressure chamber 10.
A constriction part 13 formed by an orifice is provided further downstream of the back pressure chamber 11 to form a low pressure part 14, and a communication passage 15 is provided between the low pressure part 14 and the back pressure chamber 11 to communicate with each other.

上記本発明の構成における流量制御型比例制御
弁の作用を次に述べる。一次圧室９の圧力をP1、
二次圧室１０圧力をP2、低圧部１４および背圧室
１１の圧力をP3とし、弁体４の受圧面積をＳV、
ダイヤフラム５の受圧面積ＳDとし、コイル６と
プランジヤ７などからなる電磁駆動部によつて弁
体４に作用させる力をＦとすると、P2−P3＝Ｆ／ＳＶ となる。 The operation of the flow rate control type proportional control valve in the configuration of the present invention described above will be described below. The pressure in the primary pressure chamber 9 is P 1 ,
The pressure of the secondary pressure chamber 10 is P 2 , the pressure of the low pressure section 14 and the back pressure chamber 11 is P 3 , the pressure receiving area of the valve body 4 is S V ,
If the pressure-receiving area of the diaphragm 5 is S D and the force exerted on the valve body 4 by the electromagnetic drive unit including the coil 6 and the plunger 7 is F, then P 2 −P 3 =F/ SV .

ただしＳV＝ＳDとなるように設計してある。し
たがつてP2−P3は電磁駆動部が発生して弁体４に
作用する力Ｆに比例して任意に制御可変できる。
ここでP2−P3は前述のごとくオリフイスによる絞
り部１３の上流と下流の圧力差である。そして一
般に知られているようにオリフイスに流体が流れ
て生ずるオリフイス前後の圧力差はその流体の流
量の関数となる。つまり弁体４に作用する力Ｆに
よりP2−P3が決まるという事はＦにより流量が決
まるということであり、一次圧室９の圧力P1やこ
の比例制御弁で燃焼量を制御されるバーナの能力
すなわちバーナノズルの口径、数には無関係であ
るということである。 However, it is designed so that S V =S D. Therefore, P 2 -P 3 can be controlled and varied as desired in proportion to the force F generated by the electromagnetic drive section and acting on the valve body 4.
Here, P 2 −P 3 is the pressure difference between the upstream and downstream of the constriction portion 13 due to the orifice, as described above. As is generally known, the pressure difference across the orifice that occurs when fluid flows through the orifice is a function of the flow rate of the fluid. In other words, the fact that P 2 - P 3 is determined by the force F acting on the valve body 4 means that the flow rate is determined by F, and the combustion amount is controlled by the pressure P 1 in the primary pressure chamber 9 and this proportional control valve. This means that it is unrelated to the capacity of the burner, that is, the diameter and number of burner nozzles.

次に本発明の一実施例として第４図の流量制御
型比例制御弁を第１図の湯沸器に用いた場合を第
５図本発明の特性図により説明する。 Next, as an embodiment of the present invention, a case where the flow rate control type proportional control valve shown in FIG. 4 is used in the water heater shown in FIG. 1 will be explained with reference to FIG. 5, which is a characteristic diagram of the present invention.

従来例の説明と同様湯沸器の負荷が十分大きく
バーナB1，B2が全能力で燃焼している状態か
ら、負荷が小さくなつて電磁弁V1が閉じバーナ
B2のみが燃焼し、さらにバーナB2の燃焼量が小
さくなつてゆく様子を第５図を用いて説明する
と、まず比例弁電流ｉ＝i1でバーナB1，B2はそれ
ぞれ全能力で燃焼しガス流量はＱ＝Q1である。
負荷が小さくなつて比例弁電流が減少されｉ＝i3
となるとバーナB1，B2も燃焼量が小さくなり、
B1，B2の合計のガス流量は曲線ａを経てＱ＝Q2
となる。この時バーナB1，B2それぞれのガス流
量は曲線a′を経てｉ＝i3のときＱ＝Q3である。 As in the conventional example, the load on the water heater is sufficiently large and burners B 1 and B 2 are burning at full capacity, but when the load decreases, solenoid valve V 1 closes and the burners
To explain how only B 2 burns and the combustion amount of burner B 2 decreases using Fig. 5, first, when the proportional valve current i = i 1 , burners B 1 and B 2 are each at full capacity. The combustion gas flow rate is Q= Q1 .
As the load decreases, the proportional valve current decreases and i=i 3
Then, the combustion amount of burners B 1 and B 2 will also become smaller,
The total gas flow rate of B 1 and B 2 is Q = Q 2 through curve a.
becomes. At this time, the gas flow rate of each of the burners B 1 and B 2 passes through the curve a', and when i=i 3 , Q=Q 3 .

ここで電磁弁V1が閉じられると第１バーナB1
は燃焼を停止し、第２バーナB2のみが燃焼を続
けるが、従来例とちがつて比例弁電流がｉ＝i3の
まゝで流量制御型比例制御弁は前述のようにガス
流量Ｑ＝Q2をを流すように作動する。従つて第
２バーナB2は電磁弁V1が開いていた時Q3のガス
流量で燃焼していたが、電磁弁V1が閉じた瞬間
Q2のガス流量で燃焼する。 Here, when the solenoid valve V 1 is closed, the first burner B 1
stops combustion, and only the second burner B2 continues combustion, but unlike the conventional example, the proportional valve current remains at i= i3 , and the flow rate control type proportional control valve changes the gas flow rate Q as described above. It operates so that = Q 2 flows. Therefore, the second burner B2 was burning at a gas flow rate of Q3 when the solenoid valve V1 was open, but at the moment when the solenoid valve V1 was closed.
Burns at a gas flow rate of Q 2 .

そしてさらに負荷が小さくなると比例弁電流が
さらに減少し、ガス流量は曲線ｂにに従つてｉ＝
i4でＱ＝Q3となる。 Then, as the load decreases further, the proportional valve current decreases further, and the gas flow rate follows curve b, i=
For i 4 , Q=Q 3 .

逆に湯沸器の負荷が増大する時はｉ＝i3で電磁
弁V1が開き、この瞬間第２バーナB2はＱ＝Q3と
なり、第１バーナB1もＱ＝Q3となり、バーナB1
とB2の合計ガス流量はＱ＝Q2となり、さらに比
例弁電流ｉが増加するとそれぞれのバーナはa′の
曲線にそつて、バーナB1とB2の合計ガス流量は
曲線ａにそつて増加し、ｉ＝i1でＱ＝Q1となる。 Conversely, when the load on the water heater increases, the solenoid valve V 1 opens at i = i 3 , and at this moment the second burner B 2 becomes Q = Q 3 , the first burner B 1 also becomes Q = Q 3 , Burner B 1
The total gas flow rate of B 1 and B 2 becomes Q = Q 2 , and as the proportional valve current i increases, each burner moves along the curve a', and the total gas flow rate of burners B 1 and B 2 moves along the curve a. increases, and when i=i 1 , Q=Q 1 .

このように本発明によれば従来例に見られた電
磁弁V1の開、閉時に生ずる不連続なガス流量制
御を全く解消し、連続的に制御することが出来
る。 As described above, according to the present invention, the discontinuous gas flow rate control that occurs when the solenoid valve V1 is opened and closed, which occurs in the conventional example, can be completely eliminated and continuous control can be performed.

第６図は本発明の実用的実施例で第５図につい
て説明した電磁弁V1の開閉にヒステリシスをも
たせたもので、電磁弁V1の頻繁な開閉を防止す
る為に比例弁電流が減少時ｉ＝ｉ3Lで電磁弁V1を
閉にし、比例弁電流が増加時ｉ＝ｉ3Hで電磁弁V1
を開にするものである。 Figure 6 shows a practical embodiment of the present invention in which hysteresis is provided in the opening and closing of the solenoid valve V 1 explained in connection with Figure 5, and the proportional valve current is reduced to prevent frequent opening and closing of the solenoid valve V 1 . When i = i 3L , solenoid valve V 1 is closed, and when the proportional valve current increases, when i = i 3H , solenoid valve V 1 is closed.
It is intended to open up the world.

以上のように本発明のガス燃焼制御装置によれ
ば次の効果が得られる。 As described above, the gas combustion control device of the present invention provides the following effects.

(1) 流量制御型比例制御弁の下流の複数のバーナ
を電磁弁の開閉により切換える構成としている
ので、バーナ本数切換時においてもガス流量の
連続的制御が可能である。(1) Since multiple burners downstream of the flow rate control type proportional control valve are switched by opening and closing a solenoid valve, continuous control of gas flow rate is possible even when switching the number of burners.

(2) 流量制御型の比例制御弁であるがゆえに、バ
ーナのノズル径寸法にばらつきがあつてもガス
流量には影響しないので、ガス流量を正確に制
御できる。(2) Since it is a flow rate control type proportional control valve, the gas flow rate is not affected even if there are variations in the burner nozzle diameter, so the gas flow rate can be controlled accurately.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は従来例および本発明共通のガス湯沸器
のシステム図、第２図は従来例のシステムに用い
られる圧力制御型比例制御弁の原理を示す構成
図、第３図は従来例の特性図、第４図は本発明の
システムに用いる流量制御型比例制御弁の原理を
示す構成図、第５図は本発明の一実施例の動作説
明図、第６図は本発明の他の実施例の動作説明図
である。 PV……比例制御弁、B1，B2……バーナ、Pr…
…分岐管、V1，V2……電磁弁、４……弁体、６
〜８……電気的駆動部、９……一次圧室、１０…
…二次圧室、５……ダイヤフラム、１１……背圧
室、１４……低圧部、１５……連通部、１３……
絞り部。 Fig. 1 is a system diagram of a gas water heater common to the conventional example and the present invention, Fig. 2 is a configuration diagram showing the principle of a pressure control type proportional control valve used in the conventional system, and Fig. 3 is a system diagram of the conventional example. FIG. 4 is a configuration diagram showing the principle of the flow rate control type proportional control valve used in the system of the present invention, FIG. 5 is an explanatory diagram of the operation of one embodiment of the present invention, and FIG. FIG. 3 is an explanatory diagram of the operation of the embodiment. PV...Proportional control valve, B 1 , B 2 ...Burner, Pr...
... Branch pipe, V 1 , V 2 ... Solenoid valve, 4 ... Valve body, 6
~8... Electric drive unit, 9... Primary pressure chamber, 10...
... Secondary pressure chamber, 5 ... Diaphragm, 11 ... Back pressure chamber, 14 ... Low pressure section, 15 ... Communication section, 13 ...
Aperture part.

Claims (1)

【特許請求の範囲】 １ ガスの流通路内に、流路断面積を可変し得る
弁体を設け、前記弁体に作用する力を発生する電
気的駆動部と、前記弁体の上流側に一次圧室、弁
体下流側に二次圧室を有し、前記弁体と連動した
ダイヤフラムの流通路と反対側に背圧室を設け、
前記二次圧室よりも下流通路の低圧部と前記背圧
室とを連通する連通路を設けた流量制御型比例制
御弁と、前記流量制御型比例制御弁の下流側に複
数のバーナと、前記バーナの数を切換える電磁弁
とからなるガス燃焼制御装置。 ２ 二次圧室と上記低圧部との間に、オリフイ
ス、あるいはノズルを設けた特許請求の範囲第１
項記載のガス燃焼制御装置。 ３ 配管抵抗による圧力降下が十分得られる箇所
を低圧部とした特許請求の範囲第１項記載のガス
燃焼制御装置。[Scope of Claims] 1. A valve body that can vary the cross-sectional area of the flow path is provided in the gas flow path, an electric drive unit that generates a force acting on the valve body, and an electric drive unit provided on the upstream side of the valve body. A primary pressure chamber, a secondary pressure chamber on the downstream side of the valve body, and a back pressure chamber on the opposite side of the flow path of the diaphragm interlocked with the valve body,
a flow rate control type proportional control valve provided with a communication passage that communicates a low pressure part of a passage downstream of the secondary pressure chamber with the back pressure chamber; a plurality of burners downstream of the flow rate control type proportional control valve; A gas combustion control device comprising a solenoid valve that switches the number of burners. 2. Claim 1, wherein an orifice or nozzle is provided between the secondary pressure chamber and the low pressure section.
Gas combustion control device as described in section. 3. The gas combustion control device according to claim 1, wherein the low-pressure portion is a location where a sufficient pressure drop due to piping resistance can be obtained.
JP56131148A 1981-08-20 1981-08-20 Gas combustion controller Granted JPS5833024A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP56131148A JPS5833024A (en) 1981-08-20 1981-08-20 Gas combustion controller

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP56131148A JPS5833024A (en) 1981-08-20 1981-08-20 Gas combustion controller

Publications (2)

Publication Number Publication Date
JPS5833024A JPS5833024A (en) 1983-02-26
JPS6154130B2 true JPS6154130B2 (en) 1986-11-20

Family

ID=15051116

Family Applications (1)

Application Number Title Priority Date Filing Date
JP56131148A Granted JPS5833024A (en) 1981-08-20 1981-08-20 Gas combustion controller

Country Status (1)

Country Link
JP (1) JPS5833024A (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02138600U (en) * 1989-04-21 1990-11-19
CN1302741C (en) * 2004-01-20 2007-03-07 松下电器产业株式会社 Electric vacuum cleaner

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61144345U (en) * 1985-02-27 1986-09-05
JPS61265410A (en) * 1985-05-20 1986-11-25 Tokyo Gas Co Ltd Method of controlling combustion device
JPS62136273U (en) * 1986-02-21 1987-08-27
JPS6374946U (en) * 1986-11-05 1988-05-18

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5244425A (en) * 1975-10-03 1977-04-07 Matsushita Electric Ind Co Ltd Gas governor
JPS5642657B2 (en) * 1974-01-28 1981-10-06

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5642657U (en) * 1979-09-04 1981-04-18

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5642657B2 (en) * 1974-01-28 1981-10-06
JPS5244425A (en) * 1975-10-03 1977-04-07 Matsushita Electric Ind Co Ltd Gas governor

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02138600U (en) * 1989-04-21 1990-11-19
CN1302741C (en) * 2004-01-20 2007-03-07 松下电器产业株式会社 Electric vacuum cleaner

Also Published As

Publication number Publication date
JPS5833024A (en) 1983-02-26

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