JPS6256439B2 - - Google Patents
Info
- Publication number
- JPS6256439B2 JPS6256439B2 JP56124135A JP12413581A JPS6256439B2 JP S6256439 B2 JPS6256439 B2 JP S6256439B2 JP 56124135 A JP56124135 A JP 56124135A JP 12413581 A JP12413581 A JP 12413581A JP S6256439 B2 JPS6256439 B2 JP S6256439B2
- Authority
- JP
- Japan
- Prior art keywords
- condenser
- pressure
- tank
- steam
- atmosphere
- 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
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Description
【発明の詳細な説明】
本発明はタービン復水設備の復水を大気開放の
タンクに排出する場合の排出方法に関する。復水
器の大気開放のタンクに排出する場合に、復水器
上流の条件により復水器上流側の圧力をある一定
の範囲に納める必要のある場合がある。このよう
な場合の例として、復水器上流側に排気圧力を大
気圧以上とするタービンを設置する場合の復水器
関係のフローを第１図に示す。タービン１３に流
入した蒸気はタービンを出た後復水器１１により
復水され大気開放のタンク１２へ戻り再度ボイラ
用水として利用される。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a method for discharging condensate from a turbine condensate facility into a tank open to the atmosphere. When discharging into a tank of a condenser that is open to the atmosphere, it may be necessary to keep the pressure upstream of the condenser within a certain range depending on the conditions upstream of the condenser. As an example of such a case, FIG. 1 shows a flow related to the condenser in the case where a turbine is installed upstream of the condenser to make the exhaust pressure equal to or higher than atmospheric pressure. After the steam that has entered the turbine 13 exits the turbine, it is condensed by the condenser 11 and returned to the tank 12, which is open to the atmosphere, to be used again as boiler water.
この場合のタービン出口蒸気圧力（ＰEと称
す）は、第１図の様に復水器１１からの復水管１
４を水面下に入れている場合には下式により決定
される。 In this case, the turbine outlet steam pressure (referred to as P
When 4 is placed under water, it is determined by the following formula.
ＰE＝ＰA＋ΔＰP1＋ΔＰC＋ΔＰP2＋Ｈ …(1)
ただしＰA：タンク１２水面にかかる大気圧、
ΔＰP1：タービン１３出口から復水器１１
までの配管の圧力損失、
ΔＰC：復水器１１内の圧力損失、
ΔＰP2：復水器１１からタンク１２までの
配管の圧力損失、
Ｈ：タンク１２水面を基準とした復水器１
１内水面までの水頭差。 P E = P A + ΔP P1 + ΔP C + ΔP P2 + H …(1) where P A : Atmospheric pressure on the water surface of tank 12, ΔP P1 : From outlet of turbine 13 to condenser 11
ΔP C : Pressure loss in condenser 11, ΔP P2 : Pressure loss in piping from condenser 11 to tank 12, H: Condenser 1 based on the water surface of tank 12
1 Difference in water head to the internal water surface.
またタンク１２内の復水管１４を水面下に入れ
ず大気に開放している場合には上記(1)式中のＨ＝
０となり、圧力損失のみでタービン出口蒸気圧力
が決定される。タービン出口蒸気圧力が計画値に
比べ低くなりすぎると蒸気の湿り度が増し、ドレ
ンアタツクなどの害が予想され、又高くなりすぎ
ると耐圧上の問題及び発電量の減少が起こり好ま
しくない。従つてタービン出口蒸気圧力は製作メ
ーカによつて異なる一定の範囲に納まるようにす
る必要がある。 In addition, if the condensate pipe 14 in the tank 12 is not placed under the water surface but is opened to the atmosphere, H =
0, and the turbine outlet steam pressure is determined only by pressure loss. If the turbine outlet steam pressure becomes too low compared to the planned value, the humidity of the steam will increase, and damage such as drain attack is expected, and if it becomes too high, problems with pressure resistance and a decrease in the amount of power generation will occur, which is undesirable. Therefore, it is necessary that the steam pressure at the turbine outlet falls within a certain range, which varies depending on the manufacturer.
このように復水器の復水を大気開放のタンクに
排出し、復水器上流側の圧力を一定の範囲に保つ
必要がある場合に従来行なわれている代表的な方
法には第２図に示すように復水器１１とタンク１
２の間の配管１４に圧力調節弁１５を設ける方法
がある。 When it is necessary to discharge the condensate from the condenser into a tank open to the atmosphere and maintain the pressure upstream of the condenser within a certain range, the typical method conventionally used is as shown in Figure 2. Condenser 11 and tank 1 as shown in
There is a method of providing a pressure regulating valve 15 in the pipe 14 between the two.
この方法によれば復水器上流側圧力を出来る限
り大気圧に近づけたい場合、弁の圧力損失を小さ
くすることが要求され大口径の調節弁が必要とな
る。 According to this method, if the pressure on the upstream side of the condenser is to be as close to atmospheric pressure as possible, it is required to reduce the pressure loss of the valve, and a large-diameter control valve is required.
また第３図に示すように復水器１１の出口配管
をタンク１２内で大気に開放する方法も使用され
る。 Alternatively, as shown in FIG. 3, a method may be used in which the outlet piping of the condenser 11 is opened to the atmosphere within the tank 12.
この方法によれば前記のように圧力損失のみで
復水器上流側圧力が決定されるから最大流量時の
圧力損失により決定される復水器上流側圧力から
流量０の時の大気圧までの変動におさえられる。 According to this method, the pressure on the upstream side of the condenser is determined only by the pressure loss as described above, so the pressure on the upstream side of the condenser determined by the pressure loss at the maximum flow rate to the atmospheric pressure when the flow rate is 0. Suppressed by fluctuations.
しかし蒸気流量の急激な減少の場合には一時的
に復水器内は真空となり配管の大気開放した部分
から空気を吸込み復水器の復水能力が低下したり
腐食の原因となることがある。 However, in the case of a sudden decrease in steam flow rate, the inside of the condenser may temporarily become vacuum and air may be sucked in from the part of the piping that is open to the atmosphere, reducing the condensing capacity of the condenser or causing corrosion. .
また配管を大気開放し第２図に示す調節方法と
組合わせたものも用いられている。上記第２図に
示す方法は調節装置が必要であり設備費及び維持
管理に費用を要する。また急激に復水器への流入
蒸気が増加し、復水能力が上まわつた場合などは
蒸気のまま流出することがあつた。 A method in which the piping is opened to the atmosphere in combination with the adjustment method shown in FIG. 2 is also used. The method shown in FIG. 2 requires an adjustment device and requires equipment costs and maintenance costs. In addition, if the amount of steam flowing into the condenser suddenly increased and the condensing capacity was exceeded, steam would sometimes flow out.
本発明は、特別な調節装置を使用することな
く、安価でかつ運転に労力を要しない方法で、な
おかつ空気の吸込みや蒸気の吹出しを防止するこ
とを目的としている。 The object of the invention is to prevent air ingestion and steam outflow in an inexpensive and effortless manner, without the use of special regulating devices.
この目的を達成するために本発明においては、
復水器中の復水を大気開放のタンクに排出する復
水器において、復水器と大気開放のタンクを持続
する配管の一部をＵ字状になし、Ｕ字部の出口側
に大気開放部を設け、空気の吸込み、蒸気の吹出
しを防止するとともに、復水器の上流側の圧力を
一定の範囲に調整することを特徴とする。 In order to achieve this purpose, in the present invention,
In a condenser that discharges condensate into a tank that is open to the atmosphere, a part of the piping that connects the condenser and the tank that is open to the atmosphere is shaped like a U, and the outlet side of the U-shaped part is connected to the atmosphere. It is characterized by having an open part to prevent air from being sucked in and steam from blowing out, and to adjust the pressure upstream of the condenser to within a certain range.
さらに、Ｕ字部の出口側に液面を一定化する大
気開放のタンクを設ければ、空気の吸込、蒸気の
吹出しを防止するとともに、復水器の上流側の圧
力を一定の範囲に調整することができる。 Furthermore, by providing a tank open to the atmosphere to stabilize the liquid level on the outlet side of the U-shaped part, it will prevent air intake and steam blow-out, and adjust the pressure on the upstream side of the condenser to a certain range. can do.
このようにして復水器への流入蒸気量が減少し
た場合、復水器内に復水が逆流し、凝縮に利用さ
れる伝熱面を減少させることができる。 When the amount of steam flowing into the condenser is reduced in this way, condensate flows back into the condenser, reducing the heat transfer surface available for condensation.
従つて、本発明によれば、特別な調節装置を使
用することなく、配管又は配管とタンクの組合せ
により、復水器上流側の圧力を一定の範囲に保つ
とともに、空気の吸込みの防止と蒸気の吹出しを
防止することができる。 Therefore, according to the present invention, the pressure on the upstream side of the condenser can be maintained within a certain range by piping or a combination of piping and a tank without using any special regulating device, and the pressure on the upstream side of the condenser can be prevented from being sucked in and steam can be prevented. can prevent blowing out.
第４図に本発明の方法による１つの実施例を示
す。 FIG. 4 shows one embodiment of the method of the present invention.
復水器１１に入つた蒸気は復水されＵ字状配管
１４′に入る。その後大気開放部すなわち排気口
１７を有する中間タンク１６に入り、オーバーフ
ローなどにより水面一定化され、復水管１４を経
て、タンク１２へ戻される。この場合の復水器上
流側蒸気圧力は式(1)同様次式にて決定される。 The steam entering the condenser 11 is condensed and enters the U-shaped pipe 14'. Thereafter, the water enters an intermediate tank 16 having an atmosphere open part, that is, an exhaust port 17, the water level is made constant by overflow, etc., and the water is returned to the tank 12 through a condensate pipe 14. In this case, the steam pressure on the upstream side of the condenser is determined by the following equation, similar to equation (1).
ＰE＝ＰA＋ΔＰP＋ΔＰC＋ΔＰU＋Ｈ …(2)
ＰE：復水器上流側蒸気圧力
ＰA：タンク３水面にかかる大気圧
ΔＰP：復水器上流から復水器１１までの配管
の圧力損失
ΔＰC：復水器１１内の圧力損失
ΔＰU：Ｕ字状配管１４′の圧力損失
Ｈ ：中間タンク１６の水面を基準とした復水
器１１内水面までの水頭差
復水器上流側蒸気圧力を0.3atg、復水器出口復
水温度を90℃として復水器入口最大流量を約
15t／ｈとする場合の計画例を以下に示す。 P E = P A + ΔP P + ΔP C + ΔP U + H …(2) P E : Steam pressure on the upstream side of the condenser P A : Atmospheric pressure on the water surface of tank 3 ΔP P : From the upstream side of the condenser to the condenser 11 Pressure loss in the piping ΔP C : Pressure loss in the condenser 11 ΔP U : Pressure loss in the U-shaped pipe 14' H : Difference in head between the water level in the condenser 11 and the water level in the intermediate tank 16 Condensate The steam pressure on the upstream side of the reactor is 0.3atg, the condensate temperature at the condenser outlet is 90℃, and the maximum flow rate at the condenser inlet is approximately
An example of a plan in the case of 15t/h is shown below.
最大流量時の各部圧力損失をΔＰP＝0.05Kg／
cm2、ΔＰC＝0.05Kg／cm2、ΔＰU＝0.01Kg／cm2とす
るとＰE＝0.3atgとするためにはＨ＝0.19Kg／cm2
つまりＵ字状配管１４′の出口に約1.9ｍの水頭圧
をかければ良い。 The pressure loss at each part at maximum flow rate is ΔP P = 0.05Kg/
cm 2 , ΔP C =0.05Kg/cm 2 , ΔP U =0.01Kg/cm 2 , in order to set P E =0.3atg, H = 0.19Kg/cm 2
In other words, it is sufficient to apply a water head pressure of approximately 1.9 m to the outlet of the U-shaped pipe 14'.
このことは最大流量時の復水器１１内水面に対
し約1.9ｍ高い位置に中間タンク１６の水面位置
となるようにすれば良いことになる。次に蒸気流
量が減少した場合を考えると蒸気流量の平方値に
反比例して各圧力損失が減少する。また復水器１
１内の復水は排出されず復水器１１内の水面は
徐々に上昇し凝縮に利用される伝熱面を減少させ
る。現実にはあり得ないが今仮に、各圧力損失値
が０で復水器１１が復水で満水状態になつてとす
ると、(2)式より復水器１１上流側蒸気圧力は水面
の水頭差のみで決定される。復水器１１の最上部
と、最大流量時の器内水面との差は通常0.5ｍ以
内であるので、満水状態でのＨは0.14Kg／cm2以上
である。従つて復水器１１上流側蒸気圧力は通常
運転時0.14atgから0.3atgの間で調節できることに
なる。急激に復水器１１に流入する蒸気流量が減
少した場合中間タンク１６から復水器１１内へ復
水が逆流するため中間タンク１６の水位が一時的
に下がる。この時の水位の低下は復水器１１の器
内圧を低下させることになるので中間タンク１６
内の水面の移動量をできる限りおさえるよう横断
面の大きいタンクとする。 This means that the water surface of the intermediate tank 16 may be positioned approximately 1.9 m higher than the water surface of the condenser 11 at maximum flow rate. Next, considering the case where the steam flow rate decreases, each pressure loss decreases in inverse proportion to the square value of the steam flow rate. Also condenser 1
The condensate in the condenser 11 is not discharged and the water level in the condenser 11 gradually rises, reducing the heat transfer surface available for condensation. Although it is impossible in reality, if each pressure loss value is 0 and the condenser 11 is filled with condensate, then from equation (2), the steam pressure on the upstream side of the condenser 11 is the head of water. Determined only by the difference. Since the difference between the top of the condenser 11 and the water level inside the condenser at maximum flow rate is usually within 0.5 m, H in a full water state is 0.14 Kg/cm 2 or more. Therefore, the steam pressure on the upstream side of the condenser 11 can be adjusted between 0.14 atg and 0.3 atg during normal operation. When the flow rate of steam flowing into the condenser 11 suddenly decreases, condensate flows back from the intermediate tank 16 into the condenser 11, so that the water level in the intermediate tank 16 temporarily decreases. The drop in water level at this time will reduce the internal pressure of the condenser 11, so the intermediate tank 16
The tank should have a large cross section to minimize the amount of movement of the water surface within the tank.
前記例の場合復水器１１の内容積は約２m3であ
るので、中間タンク１６容量を５m3とし直径を２
ｍの円筒縦形タンクとすると復水器１１内に２m3
の復水が逆流した場合、一時的に中間タンク１６
内水位は約0.64ｍ下がる。この時の復水器上流側
蒸気圧力は水頭差が0.076Kg／cm2となるので、
0.076atgとなる。 In the above example, the internal volume of the condenser 11 is approximately 2 m 3 , so the intermediate tank 16 capacity is 5 m 3 and the diameter is 2 m 3 .
m cylindrical vertical tank, there will be 2 m 3 in the condenser 11.
If the condensate flows back, temporarily remove the intermediate tank 16.
The internal water level will drop by approximately 0.64m. At this time, the steam pressure on the upstream side of the condenser has a water head difference of 0.076Kg/ cm2 , so
It becomes 0.076atg.
従つて本装置による制御範囲は、通常運転時
0.14〜0.3atg、瞬時0.076〜0.3atgとなる。 Therefore, the control range of this device is during normal operation.
0.14 to 0.3 atg, instantaneous 0.076 to 0.3 atg.
一方復水器１１に流入する蒸気が瞬時計画値を
上まつた場合、復水器１１の上流側の蒸気圧力が
上昇する。蒸気圧力が上昇した場合復水器１１の
出口側に設けられたＵ字状配管１４′の入口側の
水面を押し下げることにより、蒸気のまま排出さ
れることを防止する。この場合の許容圧力はＵ字
状配管１４′の最下部と中間タンク１６の水平の
水頭差までである。 On the other hand, when the steam flowing into the condenser 11 exceeds the instantaneous planned value, the steam pressure on the upstream side of the condenser 11 increases. When the steam pressure increases, the water level on the inlet side of the U-shaped pipe 14' provided at the outlet side of the condenser 11 is pushed down to prevent the steam from being discharged as it is. In this case, the permissible pressure is up to the horizontal water head difference between the bottom of the U-shaped pipe 14' and the intermediate tank 16.
また復水器１１への流入蒸気量の変動が急激で
ない場合、又は復水器上流側蒸気圧力が瞬時真空
となることが許容される場合には中間タンク１６
は省略できる。その実施例を前例の場合にそつて
第５図に示す。なお各機器名称は第４図と同一で
ある。 In addition, if the fluctuation in the amount of steam flowing into the condenser 11 is not sudden, or if the steam pressure on the upstream side of the condenser is allowed to become an instantaneous vacuum, the intermediate tank 16
can be omitted. The embodiment is shown in FIG. 5 along with the previous example. Note that the names of each device are the same as in FIG. 4.
また第４図において一部復水をタンク１２より
ポンプ等を使用し、戻すなどして中間タンク１６
内を一定水面とすると、急激な蒸気流量変動の場
合でも前例の場合0.14〜0.3atgの範囲の圧力変動
にとどめることができる。 In addition, in Fig. 4, some of the condensate is returned to the intermediate tank 16 using a pump or the like from the tank 12.
Assuming a constant water level inside, even in the case of rapid steam flow rate fluctuations, pressure fluctuations can be kept within the range of 0.14 to 0.3 atg in the case of the previous example.
第１図、第２図および第３図は、それぞれ異な
つた復水を大気開放のタンクに排出する従来の系
統の接続図、第４図および第５図は本発明による
方法のそれぞれ異なつた接続図である。
１１…復水器、１２…タンク、１３…タービ
ン、１４…復水管、１４′…Ｕ字状配管、１６…
中間タンク、１７…大気開放部または排出口。
1, 2 and 3 are connection diagrams of conventional systems for discharging different types of condensate into tanks open to the atmosphere, and FIGS. 4 and 5 are connection diagrams of different connections of the method according to the invention, respectively. It is a diagram. 11... Condenser, 12... Tank, 13... Turbine, 14... Condensate pipe, 14'... U-shaped piping, 16...
Intermediate tank, 17...atmosphere opening or discharge port.
Claims (1)
クへ排出する方法において、復水器を大気開放の
タンクに接続する配管の一部をＵ字状にして、こ
のＵ字部の出口側に大気開放部を設け復水器上流
側の圧力を一定範囲に保つことを特徴とする、復
水を大気開放のタンクに排出する方法。1. In a method of discharging condensate from a turbine condensation equipment to a tank open to the atmosphere, a part of the piping that connects the condenser to the tank open to the atmosphere is made into a U shape, and the outlet side of this U shape is A method for discharging condensate into a tank that is open to the atmosphere, which is characterized by providing an atmosphere open section and maintaining the pressure on the upstream side of the condenser within a certain range.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12413581A JPS5826991A (en) | 1981-08-10 | 1981-08-10 | Method of discharging condensed water into tank opened to atmosphere |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12413581A JPS5826991A (en) | 1981-08-10 | 1981-08-10 | Method of discharging condensed water into tank opened to atmosphere |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5826991A JPS5826991A (en) | 1983-02-17 |
| JPS6256439B2 true JPS6256439B2 (en) | 1987-11-25 |
Family
ID=14877783
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12413581A Granted JPS5826991A (en) | 1981-08-10 | 1981-08-10 | Method of discharging condensed water into tank opened to atmosphere |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5826991A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0324359A (en) * | 1989-06-19 | 1991-02-01 | Komatsu Forklift Co Ltd | Clutch control device of industrial vehicle |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5856500Y2 (en) * | 1977-06-13 | 1983-12-27 | 三洋電機株式会社 | Operation control device for ventilation fans, etc. |
-
1981
- 1981-08-10 JP JP12413581A patent/JPS5826991A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0324359A (en) * | 1989-06-19 | 1991-02-01 | Komatsu Forklift Co Ltd | Clutch control device of industrial vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5826991A (en) | 1983-02-17 |
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