JPH0345317B2 - - Google Patents
Info
- Publication number
- JPH0345317B2 JPH0345317B2 JP62311027A JP31102787A JPH0345317B2 JP H0345317 B2 JPH0345317 B2 JP H0345317B2 JP 62311027 A JP62311027 A JP 62311027A JP 31102787 A JP31102787 A JP 31102787A JP H0345317 B2 JPH0345317 B2 JP H0345317B2
- Authority
- JP
- Japan
- Prior art keywords
- flow rate
- hot water
- control valve
- temperature
- water
- 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 - Lifetime
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 143
- 238000004519 manufacturing process Methods 0.000 claims description 16
- 239000008400 supply water Substances 0.000 claims description 3
- 238000002347 injection Methods 0.000 description 9
- 239000007924 injection Substances 0.000 description 9
- 238000010586 diagram Methods 0.000 description 5
- 238000009834 vaporization Methods 0.000 description 5
- 230000008016 vaporization Effects 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000011084 recovery Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000012544 monitoring process Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000004880 explosion Methods 0.000 description 1
- 239000008236 heating water Substances 0.000 description 1
- 230000000116 mitigating effect Effects 0.000 description 1
- 238000005381 potential energy Methods 0.000 description 1
- 230000001681 protective effect Effects 0.000 description 1
- 238000005070 sampling Methods 0.000 description 1
Classifications
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
- Y02P70/10—Greenhouse gas [GHG] capture, material saving, heat recovery or other energy efficient measures, e.g. motor control, characterised by manufacturing processes, e.g. for rolling metal or metal working
Landscapes
- Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は、熱交換器を利用した排ガス顕熱に
よる温水製造設備に関する。DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to hot water production equipment using sensible heat from exhaust gas using a heat exchanger.
第４図は温水製造設備の従来例を示すブロツク
図である。同図において、１は流量センサ、２は
流量調節計、３は流量調節弁、４は温度センサ、
５は温度調節計、６は温度調節弁、７は注水レベ
ルセンサ、８は注水レベル調節計、９は注水レベ
ルオン・オフ（ON・OFF）弁、１０は循環水レ
ベルセンサ、１１は循環水レベル調節計、１２は
循環水レベル調節弁、１３は注水ポンプ、１４は
循環ポンプ、１５は注水ポンプ、１６はバツフア
タンク、１７は熱交換器である。
FIG. 4 is a block diagram showing a conventional example of hot water production equipment. In the figure, 1 is a flow rate sensor, 2 is a flow rate controller, 3 is a flow rate control valve, 4 is a temperature sensor,
5 is a temperature controller, 6 is a temperature control valve, 7 is a water injection level sensor, 8 is a water injection level controller, 9 is a water injection level on/off (ON/OFF) valve, 10 is a circulating water level sensor, 11 is a circulating water 12 is a level controller, 12 is a circulating water level control valve, 13 is a water injection pump, 14 is a circulation pump, 15 is a water injection pump, 16 is a buffer tank, and 17 is a heat exchanger.
排ガス等の顕熱を熱交換器により回収する設備
では、排ガス（熱源）自体の温度コントロールは
非常に困難なため、通常は行われない。そこで、
第４図のようにバツフアタンク１６に対し、注水
ループ、熱回収循環ループおよび送水ループを設
けて所望する量の温水を得るようにしている。
こゝに、注水ループではセンサ、７、調節計８お
よび弁９等によりタンク１６への注水レベルの制
御が行われ、熱回収循環ループではセンサ１０、
調節計１１および弁１２等により循環水レベルの
制御が行われる。また、送水ループではセンサ
４、調節計５および弁６等による温度制御と、セ
ンサ１、調節計２および弁３による流量制御とが
行われる。なお、熱回収循環ループは熱交換器１
７の熱交換率が高くなり過ぎないようにするため
の、保護ループを形成する。 In equipment that uses a heat exchanger to recover sensible heat from exhaust gas, etc., temperature control of the exhaust gas (heat source) itself is extremely difficult, so this is not normally done. Therefore,
As shown in FIG. 4, the buffer tank 16 is provided with a water injection loop, a heat recovery circulation loop, and a water supply loop to obtain a desired amount of hot water.
Here, in the water injection loop, the level of water injection into the tank 16 is controlled by the sensor 7, the controller 8, the valve 9, etc., and in the heat recovery circulation loop, the sensor 10,
The circulating water level is controlled by a controller 11, a valve 12, and the like. Further, in the water supply loop, temperature control is performed by the sensor 4, controller 5, valve 6, etc., and flow rate control is performed by the sensor 1, controller 2, and valve 3. Note that the heat recovery circulation loop is connected to heat exchanger 1.
A protective loop is formed to prevent the heat exchange rate of No. 7 from becoming too high.
しかしながら、上記のような設備ではバツフア
タンクが必要となるだけでなく、注水ループ、熱
回収循環ループおよび送水ループを独立して存在
させるため、供給ポンプ（第４図の符号１３，１
４およ１５参照）も３式必要となつて設備規模が
増大し、少量の温水要求設備としては採算性に欠
けると云う問題がある。
However, in the above-mentioned equipment, not only a buffer tank is required, but also a supply pump (numerals 13 and 1 in Fig.
4 and 15) also require three sets, which increases the scale of the equipment, and there is a problem that it is unprofitable as equipment that requires a small amount of hot water.
したがつて、この発明はバツフアタンクを削除
することによつてそのレベル制御系を削除し、送
水ポンプ台数を減少させて設備規模の著しい小型
化を図るとゝもに、中、高流域での供給水（冷
水）に対しては所定温度の温水化を実現し、低流
量域においては冷水のままの流量を確保する如
き、所定流量の確保を大前提とした簡易な限定温
水製造設備を提供することを目的とする。 Therefore, this invention eliminates the level control system by eliminating the buffer tank, reduces the number of water pumps, significantly downsizes the scale of the equipment, and improves supply in medium and high water areas. To provide a simple limited hot water production facility based on the main premise of securing a predetermined flow rate, such as heating water (cold water) to a predetermined temperature and securing the flow rate of cold water in a low flow range. The purpose is to
冷水を温水化する熱交換機と、該熱交換器に冷
水を供給する供給路と、熱交換器からの温水を外
部に送水する送水路と、前記供給路内に設けら
れ、冷水の流量調節および遮断を行なう第１の調
節弁と、前記送水路と供給路との間に設けられ、
温水の温度調節および流量調節を行う第２の調節
弁と、前記送水路を介して外部に送水される温水
の流量を制御する流量調節計と、該温水の温度を
制御する温度調節計と、前記熱交換器にて蒸気化
される供給水を放散させるための放散回路とを設
け、前記流量調節計の出力にもとづき熱交換器へ
与えられる供給水の流量実際値を予測し、
該流量実際値が所定値を越えるときは前記流量
調節計およ温度調節計により第１，第２の調節弁
を制御して所定の温度制御および流量制御を行
い、
前記流量実際値が所定値以下のときは第１調節
弁を閉じるとゝもに第２調節弁を制御して所定流
量の冷水をそのまゝ外部へ送水する一方、前記放
散回路を介して蒸気を放散する。
A heat exchanger that heats cold water, a supply path that supplies cold water to the heat exchanger, a water supply path that sends hot water from the heat exchanger to the outside, and a heat exchanger that is provided in the supply path and that controls the flow rate of cold water and provided between a first control valve that performs shutoff and the water supply channel and the supply channel,
a second control valve that adjusts the temperature and flow rate of hot water; a flow rate controller that controls the flow rate of hot water sent to the outside via the water supply channel; and a temperature controller that controls the temperature of the hot water; a dissipation circuit for dissipating the feed water vaporized in the heat exchanger, and predicting the actual flow rate of the feed water given to the heat exchanger based on the output of the flow rate controller; When the value exceeds a predetermined value, the flow rate controller and temperature controller control the first and second control valves to perform predetermined temperature control and flow rate control, and when the actual flow rate value is less than the predetermined value. When the first control valve is closed, the second control valve is controlled to directly send a predetermined flow rate of cold water to the outside, while dissipating steam through the dissipation circuit.
この発明はバツフアタンクを削除しても、温度
制御と流量制御を一元管理できる様にしたもので
ある。バツフアタンクを設けない温水制造システ
ムでは、使用側へ送水する流量制御と所定温度の
温水制造制御を同系列にて制御する必要があり、
その際下記問題が発生する。
This invention makes it possible to centrally manage temperature control and flow rate control even if the buffer tank is removed. In a hot water production system that does not include a buffer tank, it is necessary to control the flow rate of water to the user and the production of hot water at a predetermined temperature in the same system.
In this case, the following problem occurs.
１ 供給水（冷水）がある一定流量以下では、熱
交換率が高くなりすぎて熱交換後の冷水が蒸気
化し、水蒸気爆発の危険性が高い。1. If the supply water (chilled water) is below a certain flow rate, the heat exchange rate becomes too high and the cold water after heat exchange turns into vapor, increasing the risk of a steam explosion.
２ 流量制御と温度制御か干渉する。2 Flow control and temperature control interfere.
そこで、１）項に対しては、本設備を小規模化
を目的とした限定温水製造設備として考え、冷水
が所定流量以下では温水化は行わず冷水のままの
流量として確保し、蒸気化した温水は放散する様
切換えるようにする。なお、この方式を実現させ
るためには、以下の〜項目の問題点をクリア
する必要がある。 Therefore, regarding item 1), we considered this facility as a limited hot water production facility for the purpose of downsizing, and when the cold water is below a predetermined flow rate, it is not heated and the flow rate is maintained as cold water, and the water is vaporized. Switch the hot water so that it dissipates. Note that in order to realize this method, it is necessary to clear the following problems.
供給水が蒸気化する低流量域の把握（熱交換
器入口流量の推定方法）
熱源が一定量の熱量を所有していると予測した
場合、熱交換される冷水が蒸気化する低流量域は
容易に算出できるが、実際に熱交換器へ供給され
る冷水の流量は測定できない。これはバツフアタ
ンクがなく、低流量域時には冷水の熱交換ライン
を遮断して蒸気化した温水を放散させているた
め、たとえば流量センサを供給路の熱交換器近傍
に設けても遮断によつて冷水が計測できないから
である。そこで、流量調節計の出力をバルブ開度
と考え、バルブ開度から流量を算出できる様なバ
ルブ開度−流量変換器を設けて擬似的な流量換算
を行うようにする。これにより熱交換ラインを使
用して冷水を温水化して送水するか、熱交換ライ
ンを遮断して冷水のまま送水するかの切換タイミ
ングが明確となる。 Understanding the low flow rate range where feed water is vaporized (method for estimating heat exchanger inlet flow rate) If it is predicted that the heat source has a certain amount of heat, the low flow rate range where the cold water being heat exchanged is vaporized is Although it is easy to calculate, the actual flow rate of cold water supplied to the heat exchanger cannot be measured. This system does not have a buffer tank, and when the flow rate is low, the cold water heat exchange line is shut off and the vaporized hot water is dissipated. Therefore, even if a flow rate sensor is installed near the heat exchanger in the supply path, for example, the cold water will not flow through the shutoff. This is because it cannot be measured. Therefore, the output of the flow rate controller is considered to be the valve opening degree, and a valve opening-flow rate converter is provided that can calculate the flow rate from the valve opening degree to perform pseudo flow rate conversion. This makes it clear when to switch between using the heat exchange line to heat the cold water and sending it, or shutting off the heat exchange line and sending the cold water as it is.
流量制御と温度制御の切換時のプロセス変動
の緩和
こゝで、温度調節弁は所定温度となる様な冷水
供給量か、または供給水が蒸気化する低流量域以
下の冷水供給量が確保可能であればよい事から、
流量調節弁よりも小口径でよい。しかし、温度
流量制御切換時において、流量調節計からの出力
が流量調節弁から温度調節弁へ切換えられる時、
口径が異なると円滑な切換とならない。そこで、
流量調節弁の開度と同換算の流量が温度調節弁の
開度で実現できる様に開度補正を行う。これは同
タイプの調節弁であれば、いわゆるバルブ選定の
ためのCv特性カーブを利用して作成する事がで
きる。また、温度→流量制御及び流量→温度制御
へと切換つた場合は、双方の調節弁が大きく動作
するため、圧力変動時の外乱が発生し制御系がな
かなか安定しない。そこで、安定タイマを設けて
ある一定時間バルブ開度を固定させる。 Mitigation of process fluctuations when switching between flow rate control and temperature control Here, the temperature control valve can ensure a cold water supply amount that maintains a predetermined temperature, or a cold water supply amount that is below the low flow rate range where the supplied water evaporates. Since it is good if
The diameter may be smaller than that of the flow control valve. However, when the output from the flow rate controller is switched from the flow rate control valve to the temperature control valve during temperature flow control switching,
If the diameters are different, smooth switching will not occur. Therefore,
The opening degree is corrected so that the flow rate equivalent to the opening degree of the flow rate control valve can be realized by the opening degree of the temperature control valve. For control valves of the same type, this can be created using the so-called Cv characteristic curve for valve selection. Furthermore, when switching from temperature to flow rate control and flow rate to temperature control, both control valves operate greatly, causing disturbances during pressure fluctuations and making it difficult to stabilize the control system. Therefore, a stability timer is provided to fix the valve opening for a certain period of time.
蒸気化した供給水（冷水）の放散回路の作成
蒸気化した温水を放散させるラインとして、高
架貯水タンクを設ける。このラインにより、蒸
気化した比重の軽い温水のみ貯水タンクへ入
り、その分の冷水が逆に温水製造ラインに戻る
様にする。このラインはポンプ等を利用してお
らず、比重変動と位置エネルギーを利用した簡
易な循環ラインとなつている。 Creation of a dissipation circuit for vaporized supply water (cold water) An elevated water storage tank will be provided as a line to dissipate vaporized hot water. Through this line, only the vaporized hot water with a light specific gravity enters the water storage tank, and the cold water is returned to the hot water production line. This line does not use a pump or the like, and is a simple circulation line that utilizes specific gravity fluctuations and potential energy.
一方、２）項の流量制御と温度制御の干渉対策
については、次のようにする。 On the other hand, measures against interference between flow rate control and temperature control in item 2) are as follows.
すなわち、流量制御を主たる目的とすると、温
度調節計出力による流量調節弁の動作は流量制御
への外乱となる。そこで、温度調節計からの弁に
対する出力変化分（調節計出力の現在値と過去値
との差分）を流量調節計の出力へ加え干渉を除く
ようにする。 That is, if the main purpose is flow control, the operation of the flow control valve based on the output of the temperature controller becomes a disturbance to the flow control. Therefore, the amount of change in the output from the temperature controller to the valve (the difference between the current value and the past value of the controller output) is added to the output of the flow rate controller to eliminate interference.
第１図はこの発明の実施例を示す全体構成図、
第２図はその制御部を詳細に示すブロツク図、第
３図は第１図または第２図に示す各バルブの動作
を説明するためのタイムチヤートである。
FIG. 1 is an overall configuration diagram showing an embodiment of the present invention;
FIG. 2 is a block diagram showing the control section in detail, and FIG. 3 is a time chart for explaining the operation of each valve shown in FIG. 1 or 2.
第１図において、１８は蒸気化温水弁、１９は
配管満水弁、２０は遮断弁、２１は高架貯水タン
クで、その他は第４図と同様である。こゝで、送
水ポンプ１３にて供給される冷水は、流量センサ
１、流量調節計（AQR）２および流量調節弁３
により所定流量を確保する様制御され、熱交換器
１７にて温水化された供給水は温度センサ４、温
度調節計（ATR）５および温度調節弁６にて冷
水と混合され、所定温度となるよう制御される。 In FIG. 1, 18 is a vaporization hot water valve, 19 is a piping filling valve, 20 is a shutoff valve, 21 is an elevated water storage tank, and the other parts are the same as in FIG. 4. Here, the cold water supplied by the water pump 13 is passed through the flow rate sensor 1, the flow rate regulator (AQR) 2, and the flow rate control valve 3.
The supplied water is controlled to ensure a predetermined flow rate, and the supplied water heated by the heat exchanger 17 is mixed with cold water by the temperature sensor 4, temperature controller (ATR) 5, and temperature control valve 6 to reach a predetermined temperature. controlled like this.
制御の詳細を第２図によつて説明する。 The details of the control will be explained with reference to FIG.
まず、流量センサ１によつて検出される流量が
Ａ＋１m3／Ｈ以上の中・高流量域にある場合につ
いて説明する。この場合には、温度センサ４の出
力（検出温度）に基づき、送出水（温水）の温度
を所定値に制御するべく、温度調節計（ATR）
５から弁開度信号Mv1を出力し、切換器２５を介
して温度調節弁６の弁開度を制御する。 First, a case where the flow rate detected by the flow rate sensor 1 is in a medium/high flow rate region of A+1 m 3 /H or more will be described. In this case, a temperature controller (ATR) is installed to control the temperature of the delivered water (hot water) to a predetermined value based on the output (detected temperature) of the temperature sensor 4.
5 outputs a valve opening signal Mv 1 to control the valve opening of the temperature control valve 6 via the switch 25.
同時に、送出水（温水）の流量が流量センサ１
によつて検出され、検出流量に基づいて流量調節
計（AQR）２が弁開度信号Mvqを出力する。と
ころで、流量センサ１は送水路に設けられてお
り、温水の流量が所定値になるように制御がおこ
なわれる。 At the same time, the flow rate of the delivered water (hot water) is measured by the flow rate sensor 1.
The flow rate controller (AQR) 2 outputs a valve opening signal Mvq based on the detected flow rate. By the way, the flow rate sensor 1 is provided in the water supply channel, and is controlled so that the flow rate of hot water becomes a predetermined value.
いま、温度センサ４によつて検出された温水の
温度が所定値よりΔTだけ高いとすると、温度調
節計５は、温度調節弁６の弁をより開くことを指
示する弁開度信号Mv1を出力して、温度調節弁６
を介して温水路にバイパスさせる冷水量を増加さ
せ、温水を冷却させて所定の温度にもたらそうと
する。これによつて、流量センサ１で検出される
温水の流量には、温度調節弁６を介してバイパス
してくる冷水量の増加が加味されて、温水流量の
増加となつて検出される。その結果、流量調節計
２の出力する弁開度信号Mvqは少さくする（調
節弁３を閉じたことを指示する）。 Now, assuming that the temperature of the hot water detected by the temperature sensor 4 is higher than the predetermined value by ΔT, the temperature controller 5 sends a valve opening signal Mv 1 that instructs the temperature control valve 6 to open more. Output and temperature control valve 6
The amount of cold water bypassed to the hot water channel is increased to cool the hot water to a predetermined temperature. As a result, the increase in the amount of cold water bypassed via the temperature control valve 6 is added to the flow rate of hot water detected by the flow rate sensor 1, and an increase in the flow rate of hot water is detected. As a result, the valve opening signal Mvq output from the flow rate controller 2 is reduced (instructing that the control valve 3 is closed).
もしもこの弁開度信号Mvqによつて流量調節
弁３の開度を制御していると、温度調節弁６がよ
り開かれる方向に制御されると、流量調節弁３は
閉じる方向に制御されることになり、温度調節弁
６を介して送水路にバイパスする流量の増加分だ
け熱交換器１７へ供給される冷水流量を減少し、
熱交換器１７の出口側の温水の温度は更に上昇す
る。 If the opening degree of the flow rate control valve 3 is controlled by this valve opening degree signal Mvq, when the temperature control valve 6 is controlled in the direction of opening more, the flow rate control valve 3 is controlled in the direction of closing. Therefore, the flow rate of cold water supplied to the heat exchanger 17 is reduced by the increase in the flow rate bypassed to the water supply channel via the temperature control valve 6,
The temperature of the hot water on the outlet side of the heat exchanger 17 further increases.
この熱交換器１７から送出される温水の温度上
昇は、ある時間遅れをもつて温度センサ４によつ
て検出され、その結果温度調節弁６は更に開か
れ、熱交換器１７入口側の冷水流量は更に減少し
て、熱交換器１７から送出される温水の温度が更
に上昇する、という悪循環が繰り返される。温度
センサ４によつて検出された温水の温度が所定値
よりΔTだけ低い場合にも同様の悪循環が繰り返
されることは、先の説明より明らかであろう。 The temperature rise of the hot water sent out from the heat exchanger 17 is detected by the temperature sensor 4 with a certain time delay, and as a result, the temperature control valve 6 is further opened, and the cold water flow rate at the inlet side of the heat exchanger 17 is detected by the temperature sensor 4 with a certain time delay. decreases further, and the temperature of the hot water sent out from the heat exchanger 17 further increases, and the vicious cycle repeats. It will be clear from the above description that the same vicious cycle is repeated even when the temperature of the hot water detected by the temperature sensor 4 is lower than the predetermined value by ΔT.
上記の悪循環を回避するために、温度センサ４
の出力に基づき温度調整計（ATR）５によつて
温水温度の現在値と過去値との偏差を監視し、こ
の偏差に対応した温度調節計５の出力変化分
ΔMv（弁開度指令に相当する信号）を温度調節計
５から出力させ、流量調節計（AQR）２と流量
調節弁３の間に設けた加算器２８において流量調
節計２が出力する弁開度信号Mvqに加算する。 In order to avoid the above vicious cycle, the temperature sensor 4
Based on the output of the temperature controller (ATR) 5, the deviation between the current value and the past value of the hot water temperature is monitored, and the output change of the temperature controller 5 corresponding to this deviation ΔMv (corresponding to the valve opening command) A signal) is output from the temperature controller 5, and added to the valve opening signal Mvq output by the flow controller 2 in an adder 28 provided between the flow controller (AQR) 2 and the flow controller 3.
温水温度が上昇した場合には出力変化分ΔMv
としてプラスの信号が、温水温度が低下した場合
には出力変化分ΔMvとしてマイナスの信号が、
弁開度信号Mvqに加算される。そうしてMvq＋
ΔMv＝Mv2なる弁開度信号によつて温度調節弁
３の弁開度を制御する。 When the hot water temperature rises, the output change ΔMv
If the hot water temperature decreases, a negative signal will be generated as the output change ΔMv.
Added to valve opening signal Mvq. Then Mvq+
The valve opening degree of the temperature control valve 3 is controlled by the valve opening degree signal ΔMv= Mv2 .
例えば、温水温度の検出値がT1であつて、こ
の値が前回のサンプリング時の値よりΔT高い値
であつたとすると、温度調節計５は、検出温度
T1と温水がその温度に制御されるべき基準値T0
との偏差に応じた弁開度信号Mv1を出力して温度
調節弁６の弁開度を制御するとともに、温度変化
分ΔT（プラス）に応じた出力変化分ΔMv（プラス
の値を持つ）を加算器２８へ出力する。 For example, if the detected value of the hot water temperature is T1, which is ΔT higher than the value at the previous sampling, the temperature controller 5 will detect the detected temperature.
T1 and the reference value T 0 at which the hot water should be controlled to the temperature
The valve opening signal Mv 1 is output according to the deviation from the temperature control valve 6 to control the valve opening degree of the temperature control valve 6, and the output change ΔMv (having a positive value) according to the temperature change ΔT (plus) is output. is output to the adder 28.
加算器２８は流量調節計２からの出力Mvqに
ΔMyを加算して弁開度信号Mv2を出力し、この
信号Mv2によつて調節弁３の開度を制御するが、
この場合、温水温度の上昇に対応して信号Mv2は
ΔMv分大きな値をもつているので、調節弁３は
ΔMv分より開く方向に制御され、従つて、弁３
を介して熱交換器１７入口側の冷水の流量低下が
防がれることになる。上記の出力変化分ΔMvを
加算することにより、温水温度が低下した場合に
は、調節弁３はΔMv分より閉じる方向に制御さ
れることになる。 The adder 28 adds ΔMy to the output Mvq from the flow rate controller 2 and outputs a valve opening signal Mv 2 , and controls the opening of the control valve 3 using this signal Mv 2 .
In this case, the signal Mv 2 has a value larger by ΔMv in response to the rise in hot water temperature, so the control valve 3 is controlled in the direction of opening by ΔMv.
This prevents a decrease in the flow rate of cold water on the inlet side of the heat exchanger 17. By adding the above output change amount ΔMv, when the hot water temperature decreases, the control valve 3 will be controlled in the direction of closing by ΔMv.
何れの場合にも、上記の技術手段により、熱交
換器１７の入口側の冷水流量が制御され、温度セ
ンサ４、温度調整計５及び温度調節弁６による温
水の温度制御によつて熱交換器１７へ供給される
冷水の流量が好ましくない方向に変化することが
抑制されるのである。 In either case, the flow rate of cold water on the inlet side of the heat exchanger 17 is controlled by the above-mentioned technical means, and the temperature of the hot water is controlled by the temperature sensor 4, the temperature controller 5, and the temperature control valve 6. This prevents the flow rate of cold water supplied to 17 from changing in an unfavorable direction.
次に、流量調節弁３を閉じ、温度調節弁６によ
つて流量調節を行う流量がＡm3／Ｈ以下の低流量
域と、上述の流量がＡ＋１m3／Ｈ以上の中・高流
量域との切り換えについて説明する。 Next, the flow rate control valve 3 is closed, and the flow rate is adjusted by the temperature control valve 6 into a low flow area where the flow rate is less than Am 3 /H, and a medium and high flow rate area where the flow rate is A+1 m 3 /H or more. The switching will be explained.
この切り換えの為にバルブ開度−流量変換器２
２、リミツタ２３、切換器２４，２５及び２９が
設けられている。加算器２８の出力Mv2はバルブ
開度−流量変換器２２において温水流量に変換さ
れ、この変換流量がリミツタ２３に入力される。
このリミツタ２３には流量下限値Ａm3／Ｈ及び流
量上限値Ａ＋１m3／Ｈがセツトされている。 For this switching, valve opening - flow rate converter 2
2, a limiter 23 and switches 24, 25 and 29 are provided. The output Mv 2 of the adder 28 is converted into a hot water flow rate in the valve opening/flow rate converter 22 , and this converted flow rate is input to the limiter 23 .
This limiter 23 is set with a flow rate lower limit value Am 3 /H and a flow rate upper limit value A+1 m 3 /H.
いま、中・高流量域にあつたものが、温水の流
量が低下してリミツタ２３の流量下限値Ａm3／Ｈ
以下になると、リミツタ２３はこれを検出して切
換信号を出力し、切換器２４，２５を切り換え
る。この切り換えにより、流量調節弁３には加算
器２８の出力に代わつて０％信号が切換器２４を
介して入力され、流量調節弁３は閉じられる。切
換器２５における切り換えによつて、温度制御弁
６への入力は温度調整計（ATR）５の出力から、
加算器２８の出力に対応した信号に切り換えら
れ、温度調節弁６を流量制御弁として用いる流量
制御に移る。但し、加算器２８の出力は調節弁３
の制御のための開度信号である。 Now, the flow rate of hot water that was in the medium/high flow range has decreased and the flow rate lower limit value of the limiter 23 is Am 3 /H.
When it becomes below, the limiter 23 detects this and outputs a switching signal to switch the switches 24 and 25. By this switching, a 0% signal is input to the flow rate control valve 3 via the switch 24 instead of the output of the adder 28, and the flow rate control valve 3 is closed. By switching the switch 25, the input to the temperature control valve 6 is from the output of the temperature regulator (ATR) 5.
The signal is switched to a signal corresponding to the output of the adder 28, and flow control is started using the temperature control valve 6 as a flow control valve. However, the output of the adder 28 is the output of the control valve 3.
This is the opening signal for controlling the
通常、弁３と弁６とはそのバルブ口径が相違し
ているので、加算器２８の出力によつて弁６を制
御するためには加算器２８の出力Mv2を弁３と弁
６とのバルブ口径の相違に応じて補正しなければ
ならない。例えば、弁３の開度（Mv2）に対応す
る流量を得るための弁６の開度がバルブ口径比に
よつて関係ずけられるような場合には、弁３の口
径をS3、弁６の口径をS6とすると補正係数は
（S3／S6）となるので、この補正係数（S3／S6）
を、加算器２８の出力Mv2によつてバルブ口径補
正器２６から読出し、乗算器２７においてMv2
（S3／S6）を演算し、これを開度制御のための信
号として調節弁３に入力する。 Normally, valves 3 and 6 have different valve diameters, so in order to control valve 6 using the output of adder 28, the output Mv 2 of adder 28 is different from that of valves 3 and 6. It must be corrected according to the difference in valve diameter. For example, if the opening degree of the valve 6 to obtain the flow rate corresponding to the opening degree (Mv 2 ) of the valve 3 is related by the valve diameter ratio, the diameter of the valve 3 is S 3 , If the aperture of 6 is S 6 , the correction coefficient is (S 3 /S 6 ), so this correction coefficient (S 3 /S 6 )
is read out from the valve diameter corrector 26 by the output Mv 2 of the adder 28, and Mv 2 is read out in the multiplier 27.
(S 3 /S 6 ) is calculated and inputted to the control valve 3 as a signal for opening control.
一般的には、弁３と弁６それぞれのCv特性カ
ーブ（バルブ開度−流量特性カーブ）を比較する
ことによつて作成される。弁３の開度をこの弁３
の開度に対応する流量が弁６によつて得られる弁
６の開度に補正するための補正係数を、弁３への
開度信号Mv2をパラメータとして、補正器２６に
記憶しておき、加算器２８の出力Mv2によつて補
正器２６から出力Mv2に対応する補正係数を読出
して乗算器２７に入力し、乗算器２７で補正係数
と出力Mv2を乗算して、その結果を切換器２５を
介して弁６へ入力する。これによつて切換えが円
滑におこなわれることにもなる。 Generally, it is created by comparing the Cv characteristic curves (valve opening-flow rate characteristic curves) of the valves 3 and 6. Adjust the opening degree of valve 3 to this valve 3.
A correction coefficient for correcting the opening of the valve 6 such that the flow rate corresponding to the opening of the valve 6 is obtained by the valve 6 is stored in the corrector 26 using the opening signal Mv 2 to the valve 3 as a parameter. , the correction coefficient corresponding to the output Mv 2 is read from the corrector 26 using the output Mv 2 of the adder 28, and inputted to the multiplier 27. The multiplier 27 multiplies the correction coefficient and the output Mv 2 , and the result is is input to the valve 6 via the switch 25. This also allows for smooth switching.
なお、温度調節弁６によつて流量調節を行う低
流量域においては、弁３は閉じられており、また
温水の温度制御は行われないのであるから、温水
の温度を考慮して流量の制御を行う必要はない。
そこで、切換器２９によつてΔMyを０％入力に
切り換えて、この０％信号をΔMvの代わりに加
算器２８に出力する。切換器２５を切り換える切
換信号はリミツタ２３より出力される。 In addition, in the low flow range where the flow rate is adjusted by the temperature control valve 6, the valve 3 is closed and the temperature of hot water is not controlled, so the flow rate is controlled by taking the temperature of the hot water into account. There is no need to do this.
Therefore, the switch 29 switches ΔMy to 0% input, and outputs this 0% signal to the adder 28 instead of ΔMv. A switching signal for switching the switch 25 is output from the limiter 23.
温水流量が、低流量域のＡm3／Ｈ以下の値から
増加して、リミツタ２３にセツトされている流量
上限値Ａ＋１m3／Ｈ以上になると、リミツタから
切換信号が切換器２４，２５及び２９に出力さ
れ、流量調節弁３による流量調節と温度調節弁６
による温水温度の調節が平行して行われる中・高
流量域の制御に復帰する。なお、この低流量域時
にはON−OFF弁１８，１９を全閉→全開として
蒸気化した温水を高架貯水タンク２１を含む放散
ラインにて放散し、ON−OFF弁２０及び流量調
節弁３を全閉にして冷水の熱交換ラインを遮断す
る。 When the hot water flow rate increases from a value below Am 3 /H in the low flow range and exceeds the flow rate upper limit value A+1m 3 /H set in the limiter 23, a switching signal is sent from the limiter to the switches 24, 25 and 29. The flow rate is controlled by the flow rate control valve 3 and the temperature control valve 6
The system returns to control in the medium and high flow rate range, where the hot water temperature is adjusted in parallel. In addition, in this low flow range, the ON-OFF valves 18 and 19 are fully closed → fully opened, and the vaporized hot water is dissipated in the dispersion line including the elevated water storage tank 21, and the ON-OFF valve 20 and flow rate control valve 3 are fully closed. Close to shut off the cold water heat exchange line.
次に、熱交換器１７への供給水（冷水）が流量
下限値Ａ〔m3／Ｈ）以下になつた後、再び復帰す
る場合の動作について、第３図を参照して説明す
る。つまり、冷水が蒸気化する低流量域Ａ〔m3／
Ｈ〕なつて温度制御から流量制御へと切換えると
きは、温度調節弁６の開度をあらかじめＡm3／Ｈ
と算出した開度に相当する出力MV1を安定監視
時間t1の間出力し、その後は通常の流量制御を行
うべく温度調節弁６を動作させる。このとき、同
図の如く弁１８，１９を開いて放散回路を形成す
る一方、弁２０を閉じて温水の送水は停止する。
その後、冷水の蒸気化低流量域からその流量が、
例えばＡ＋１〔m3／Ｈ〕に復帰すると、流量制御
から温度制御へと切換えるべく、流量調節弁３の
開度をあらかじめＡ＋１〔m3／Ｈ〕と算出した開
度に相当する出力MV2を安定監視時間t2の間出力
し、その後は通常の流量制御をして流量調節弁３
を動作させる。こうして、切換時の制御動作を安
定化する。なお、温度制御の流量制御時への干渉
に対する対策として、温度調節計５の出力変化分
ΔMvを加算器２８にて流量調節計出力へ加える。
但し、冷水の蒸気化低流量域では温度制御は行わ
ないため、切換器２９を介する出力変化分を加算
しないことは、既に説明した通りである。 Next, the operation when the water (chilled water) supplied to the heat exchanger 17 returns to the normal state after becoming lower than the flow rate lower limit value A [m 3 /H] will be described with reference to FIG. 3. In other words, the low flow rate area A [m 3 /
H] When switching from temperature control to flow rate control, the opening degree of the temperature control valve 6 should be adjusted in advance to Am 3 /H.
The output MV 1 corresponding to the calculated opening is output during the stability monitoring time t 1 , and thereafter the temperature control valve 6 is operated to perform normal flow control. At this time, as shown in the figure, valves 18 and 19 are opened to form a dissipation circuit, while valve 20 is closed to stop supplying hot water.
After that, the flow rate from the cold water vaporization low flow area is
For example, when returning to A+1 [m 3 /H], in order to switch from flow rate control to temperature control, the output MV 2 corresponding to the opening degree calculated in advance as A+1 [m 3 /H] is set to the opening degree of the flow rate control valve 3 . Outputs for stability monitoring time t 2 , then performs normal flow control and closes flow control valve 3.
make it work. In this way, the control operation at the time of switching is stabilized. As a measure against interference of temperature control with flow rate control, an adder 28 adds the change in the output of the temperature controller 5 ΔMv to the output of the flow rate controller.
However, as described above, since temperature control is not performed in the cold water vaporization low flow rate region, the output change via the switch 29 is not added.
この発明によればバツフアタンクを必要としな
いためポンプが１式で済み、且つポンプトリツプ
等のシーケンス回路も簡略化でき、更にバツフア
タンク廻りのレベル制御が不要となるためセンサ
の削減及び設備規模縮小化の実現が可能である。
但し、安定した温水製造システムとするには、蒸
気化低流量域時を勘案し、温水として必要な常用
流量がその低流量域に入らないよう、配管サイズ
及び熱交換器の選択が必要となる。
According to this invention, a buffer tank is not required, so only one pump is required, and sequence circuits such as pump trips can be simplified.Furthermore, level control around the buffer tank is not required, so the number of sensors and equipment size can be reduced. is possible.
However, in order to create a stable hot water production system, it is necessary to take into account the low flow rate range for vaporization and select the piping size and heat exchanger so that the regular flow rate required for hot water does not fall within that low flow rate range. .
第１図はこの発明の実施例を示す全体構成図、
第２図はその制御部を詳細に示すブロツク図、第
３図は第１図または第２図に示す各バルブの動作
を説明するためのタイムチヤート、第４図は従来
の温水製造設備の一例を示すブロツク図である。
符号説明、１…流量センサ、２…流量調節計、
３…流量調節弁、４…温度センサ、５…温度調節
計、６…温度調節弁、１３…注水ポンプ、１７…
熱交換器、１８…蒸気化温水放散弁、１９…配管
満水弁、２０…遮断弁、２１…高架貯水タンク、
２２…バルブ開度−流量換算器、２３…リミツ
タ、２４，２５，２９…切換器、２６…バルブ口
径補正器、２７…乗算器、２８…加算器。
FIG. 1 is an overall configuration diagram showing an embodiment of the present invention;
Fig. 2 is a block diagram showing the control section in detail, Fig. 3 is a time chart for explaining the operation of each valve shown in Fig. 1 or Fig. 2, and Fig. 4 is an example of conventional hot water production equipment. FIG. Symbol explanation, 1...Flow rate sensor, 2...Flow rate controller,
3...Flow control valve, 4...Temperature sensor, 5...Temperature controller, 6...Temperature control valve, 13...Water injection pump, 17...
Heat exchanger, 18... Vaporization hot water dissipation valve, 19... Piping full valve, 20... Shutoff valve, 21... Elevated water storage tank,
22... Valve opening-flow rate converter, 23... Limiter, 24, 25, 29... Switcher, 26... Valve diameter corrector, 27... Multiplier, 28... Adder.
Claims (1)
器に冷水を供給する供給路と、 熱交換器からの温水を外部に送水する送水路
と、 前記供給路内に設けられ、冷水の流量調節およ
び遮断を行う第１の調節弁３と、 前記送水路と供給路との間に設けられ、温水の
温度調節および流量調節を行う第２の調節弁６
と、 前記送水路を介して外部に送水される温水の流
量を制御する流量調節計２と、 該温水の温度を制御する温度調節計５と、 前記熱交換器にて蒸気化される供給水を放散さ
せるための放散回路１８，２１，１９と、 を備え、 前記流量調節計の出力にもとづき熱交換器へ与
えられる供給水の流量実際値を予測し、 該流量実際値が所定値を越えるときである中・
高流量域時は前記流量調節計および温度調節計に
より第１、第２の調節弁を制御して前記温水の流
量制御および温度制御を行い、 前記流量実際値が所定値以下のときである低流
量域時は第１調節弁３を閉じるとともに第２調節
弁６を制御して所定流量の冷水をそのまま外部へ
送水する一方、前記放散回路を介して蒸気を放散
するようになしたことを特徴とする温水製造設
備。 ２ 特許請求の範囲第１項に記載の温水製造設備
において、前記中・高流量域時には、第２の調節
弁６による温度制御の第１の調節弁３による流量
制御への波及を抑制するべく、温度調節計の出力
変化分を流量調節計出力に加算し、この加算結果
に基づいて第１の調節弁３を制御するようになし
たことを特徴とする温水製造設備。 ３ 特許請求の範囲第１項または第２項に記載の
温水製造設備において、前記低流量域時と中・高
流量域時相互の切換えにあたつては、前記第１，
第２調節弁の開度を所定時間だけ一定に保持する
ようになしたことを特徴とする温水製造設備。 ４ 特許請求の範囲第１項ないし第３項のいずれ
かに記載の温水製造設備において、前記第１、第
２調節弁の口径が互いに異なるときは、低流量域
時において、流量調節計２の出力に対応する第１
調節弁の開度と同換算の流量を第２調節弁におい
て得るべく、前記流量調節計の出力を補正して、
この補正結果に基づいて前記第２調節弁の開度制
御を行うようになしたことを特徴とする温水製造
設備。[Scope of Claims] 1. A heat exchanger 17 that heats cold water, a supply path that supplies cold water to the heat exchanger, a water supply path that sends hot water from the heat exchanger to the outside, and within the supply path. A first control valve 3 provided between the water supply channel and the supply channel to adjust the flow rate and cut off the cold water; and a second control valve 6 provided between the water supply channel and the supply channel to control the temperature and flow rate of the hot water.
, a flow rate controller 2 that controls the flow rate of hot water sent to the outside via the water supply channel, a temperature controller 5 that controls the temperature of the hot water, and supply water that is vaporized in the heat exchanger. and dissipation circuits 18, 21, and 19 for dissipating water, and predicts the actual flow rate of the water supplied to the heat exchanger based on the output of the flow rate controller, and when the actual flow value exceeds a predetermined value. During the time...
In the high flow range, the flow rate controller and temperature controller control the first and second control valves to control the flow rate and temperature of the hot water, and when the actual flow rate is below a predetermined value, In the flow rate range, the first control valve 3 is closed and the second control valve 6 is controlled to directly send cold water at a predetermined flow rate to the outside, while dissipating steam via the dissipation circuit. hot water production equipment. 2. In the hot water production equipment according to claim 1, in the medium/high flow rate region, in order to suppress the influence of the temperature control by the second control valve 6 on the flow rate control by the first control valve 3. A hot water production facility characterized in that a change in the output of the temperature controller is added to the output of the flow rate controller, and the first control valve 3 is controlled based on the addition result. 3. In the hot water production equipment according to claim 1 or 2, when switching between the low flow rate range and the medium/high flow rate range, the first,
A hot water production facility characterized in that the opening degree of the second control valve is held constant for a predetermined period of time. 4. In the hot water production equipment according to any one of claims 1 to 3, when the diameters of the first and second control valves are different from each other, the flow rate controller 2 is The first corresponding to the output
Correcting the output of the flow rate controller in order to obtain a flow rate equivalent to the opening degree of the control valve at the second control valve,
A hot water production facility characterized in that the opening degree of the second control valve is controlled based on the correction result.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62311027A JPH01155142A (en) | 1987-12-10 | 1987-12-10 | Hot-water producing facility |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP62311027A JPH01155142A (en) | 1987-12-10 | 1987-12-10 | Hot-water producing facility |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH01155142A JPH01155142A (en) | 1989-06-19 |
| JPH0345317B2 true JPH0345317B2 (en) | 1991-07-10 |
Family
ID=18012231
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP62311027A Granted JPH01155142A (en) | 1987-12-10 | 1987-12-10 | Hot-water producing facility |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH01155142A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111237082B (en) * | 2020-01-19 | 2022-07-29 | 山东速力动力科技有限公司 | Waste heat recovery device of gas generator set |
-
1987
- 1987-12-10 JP JP62311027A patent/JPH01155142A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01155142A (en) | 1989-06-19 |
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