JPH0583828B2 - - Google Patents
Info
- Publication number
- JPH0583828B2 JPH0583828B2 JP15103085A JP15103085A JPH0583828B2 JP H0583828 B2 JPH0583828 B2 JP H0583828B2 JP 15103085 A JP15103085 A JP 15103085A JP 15103085 A JP15103085 A JP 15103085A JP H0583828 B2 JPH0583828 B2 JP H0583828B2
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- generator
- absorption liquid
- heat source
- low
- 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
- 238000010521 absorption reaction Methods 0.000 claims description 84
- 239000007788 liquid Substances 0.000 claims description 65
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 28
- 239000006096 absorbing agent Substances 0.000 claims description 18
- 239000002912 waste gas Substances 0.000 claims description 16
- 239000003507 refrigerant Substances 0.000 claims description 15
- 230000000694 effects Effects 0.000 claims description 7
- 230000007423 decrease Effects 0.000 description 13
- 238000005057 refrigeration Methods 0.000 description 10
- 238000002485 combustion reaction Methods 0.000 description 6
- 239000000498 cooling water Substances 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 5
- 238000013021 overheating Methods 0.000 description 5
- 238000009835 boiling Methods 0.000 description 3
- 230000006866 deterioration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 239000012141 concentrate Substances 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Landscapes
- Sorption Type Refrigeration Machines (AREA)
Description
【発明の詳細な説明】
(イ) 産業上の利用分野
本発明はエンジンの廃ガスの熱とエンジンのジ
ヤケツト温水の熱を利用して運転する一重二重効
用吸収冷凍機（以下、この種の吸収冷凍機とい
う）に関する。[Detailed Description of the Invention] (a) Field of Industrial Application The present invention relates to a single-double effect absorption refrigerator (hereinafter referred to as this type of absorption refrigerator).
(ロ) 従来の技術
この種の吸収冷凍機の従来の技術として、例え
ば特開昭58−69375号公報にみられるように、エ
ンジンのジヤケツト温水で加熱される低温熱源用
発生器、溶液熱交換器および吸収器を結ぶ吸収液
の循環路とエンジンの廃ガスで加熱される高温発
生器、低温発生器、溶液熱交換器および吸収器を
結ぶ吸収液の循環路とを並列に形成することによ
り、一重効用と二重効用の吸収冷凍サイクルを形
成させて冷水を得るようにしたものが知られてい
る。(b) Prior Art Conventional technologies for this type of absorption refrigerator include, for example, a generator for a low-temperature heat source heated by engine jacket hot water, and a solution heat exchanger, as seen in Japanese Patent Application Laid-Open No. 58-69375. By forming in parallel an absorption liquid circulation path that connects the absorber and the absorber with an absorption liquid circulation path that connects the high temperature generator heated by engine waste gas, the low temperature generator, the solution heat exchanger, and the absorber. It is known that cold water is obtained by forming single-effect and double-effect absorption refrigeration cycles.
(ハ) 発明が解決しようとする問題点
上記のような従来のこの種の吸収冷凍機におい
ては、例えばエンジン側の負荷の低下に合わせて
エンジンの動力が弱められた場合、エンジンから
流出する廃ガスやジヤケツト温水のエンタルピー
が小さくなるので、廃ガスや温水の熱の大部分が
発生器内の吸収液の昇温のために消費されてその
濃縮〔冷媒の発生〕が不十分となり、この種の吸
収冷凍機の運転効率が著しく悪くなる問題点を有
していた。また、この場合、低温熱源用発生器内
の吸収液が加熱不足により過度に降温することも
あり、その影響で低温熱源用発生器から流出する
温水言い代えればエンジンへ戻る冷却水の温度が
過度に低下してエンジンの冷え過ぎを引起す問題
点もある。なお、逆の場合には、エンジンの過熱
を引起すおそれがある。(c) Problems to be solved by the invention In the conventional absorption chiller of this type described above, for example, when the power of the engine is weakened in accordance with a decrease in the load on the engine side, the waste flowing out from the engine is Since the enthalpy of the gas and jacket hot water becomes smaller, most of the heat of the waste gas and hot water is consumed to raise the temperature of the absorption liquid in the generator, and its concentration (generation of refrigerant) is insufficient, causing this type of The problem was that the operating efficiency of the absorption chiller deteriorated significantly. In addition, in this case, the temperature of the absorption liquid in the low-temperature heat source generator may drop excessively due to insufficient heating, and as a result, the temperature of the hot water that flows out of the low-temperature heat source generator, or in other words, the temperature of the cooling water that returns to the engine, becomes excessive. There is also the problem that the temperature decreases, causing the engine to become too cold. Note that in the opposite case, there is a risk of causing overheating of the engine.
本発明は、これらの問題点に鑑み、運転効率の
低下を軽減し得ると共にエンジンの冷え過ぎや過
熱を防止し得るこの種の吸収冷凍機の提供を目的
としたものである。 In view of these problems, it is an object of the present invention to provide an absorption refrigerating machine of this type that can reduce the decrease in operating efficiency and prevent the engine from becoming too cold or overheating.
(ニ) 問題点を解決するための手段
本発明は、上記の問題点を解決する手段とし
て、一重効用と二重効用の吸収冷凍サイクルを並
列に形成させて運転するこの種の吸収冷凍機にお
いて、低温熱源用発生器内の蒸気圧や液温やこの
発生器から流出する温水の温度あるいは高温発生
器内の液温や蒸気圧や高温発生器から排出される
廃ガスの温度などこれら発生器に関連する物理量
を検知しつつ吸収器から低温熱源用発生器への吸
収液流量を調節する制御装置と吸収器から高温発
生器への吸収液流量を調節する制御装置とを備え
る構成としたものである。(d) Means for Solving the Problems The present invention, as a means for solving the above-mentioned problems, provides for an absorption refrigerating machine of this type in which single-effect and double-effect absorption refrigeration cycles are formed and operated in parallel. , vapor pressure and liquid temperature in the low-temperature heat source generator, temperature of hot water flowing out from this generator, liquid temperature and vapor pressure in the high-temperature generator, temperature of waste gas discharged from the high-temperature generator, etc. A control device that adjusts the flow rate of the absorption liquid from the absorber to the low-temperature heat source generator while detecting physical quantities related to the above, and a control device that adjusts the flow rate of the absorption liquid from the absorber to the high-temperature generator. It is.
(ホ) 作用
本発明の吸収冷凍機においては、例えばエンジ
ンの動力が弱められて高温発生器、低温熱源用発
生器にそれぞれ供給される廃ガス、温水のエンタ
ルピーが小さくなるに伴ないこれら発生器内の液
温や蒸気圧などが降下し始めた場合、それに応じ
てこれら発生器へ送る吸収液の流量を減らすこと
により、吸収液が沸騰温度まで昇温するための熱
量消費（顕熱消費）を少なくして廃ガスや温水の
熱の大部分を吸収液の濃縮〔冷媒蒸気の発生〕に
消費させる働き（作用）があるので、その運転効
率の悪化を防ぐことが可能であると共に、これら
発生器内の吸収液の濃度、飽和温度、飽和蒸気圧
をエンジン動力の弱められる以前と同程度に復帰
させてエンジンの冷え過ぎを防ぐことが可能であ
る。また、逆にエンジンの動力が強められた場合
にはこの種の吸収冷凍機の運転効率を良好に維持
しつつエンジンの過熱を防ぐことができる。(E) Effect In the absorption refrigerator of the present invention, for example, as the power of the engine is weakened and the enthalpy of waste gas and hot water supplied to the high-temperature generator and low-temperature heat source generator, respectively, becomes smaller, these generators When the liquid temperature and vapor pressure start to drop, the amount of heat consumed (sensible heat consumption) to raise the temperature of the absorption liquid to boiling temperature can be reduced by reducing the flow rate of the absorption liquid sent to these generators accordingly. Since it has the function of reducing the heat of waste gas and hot water and consuming most of the heat of the absorption liquid (generation of refrigerant vapor), it is possible to prevent the deterioration of the operating efficiency and to reduce the It is possible to prevent the engine from becoming too cold by restoring the concentration, saturation temperature, and saturation vapor pressure of the absorption liquid in the generator to the same level as before the engine power was weakened. Conversely, when the power of the engine is increased, it is possible to prevent the engine from overheating while maintaining good operating efficiency of this type of absorption refrigerator.
かつまた、本発明の吸収冷凍機においては、一
重効用と二重効用の吸収冷凍サイクルを並列に形
成させて運転するようにしたものであるから、低
温熱源用発生器側への吸収液の送り量と高温発生
器側への吸収液の送り量とを別個に独立させて制
御することが可能である。このため、圧力変化の
度合の異なる高温発生器と低温熱源用発生器とを
例えば直列に結んでこれら発生器へ吸収液をシリ
ーズに送る従来のこの種の吸収冷凍機〔例れば特
開昭58−86359号公報参照〕のようにこれら発生
器での吸収液の出入のバランスを調整するための
複雑な制御も不要であり、本発明の吸収冷凍機は
簡便な制御で済むという利点をもつ。 Furthermore, in the absorption refrigerating machine of the present invention, single-effect and dual-effect absorption refrigeration cycles are formed and operated in parallel, so that the absorption liquid is not sent to the low-temperature heat source generator side. It is possible to control the amount and the amount of absorption liquid sent to the high temperature generator side separately and independently. For this reason, conventional absorption refrigerators of this type connect a high-temperature generator with different degrees of pressure change and a low-temperature heat source generator in series, and send absorption liquid to these generators in series. No. 58-86359] does not require complicated control to adjust the balance of absorption liquid in and out of these generators, and the absorption refrigerator of the present invention has the advantage of requiring simple control. .
(ヘ) 実施例
図面は本発明によるこの種の吸収冷凍機の一実
施例を示した概略構成説明図であり、１は高温の
燃焼廃ガスを熱源とする高温発生器、２はエンジ
ン冷却水言い代えればエンジンジヤケツトから流
出する低温の温水を熱源とする低温熱源用発生器
３および高温発生器１からの冷媒を熱源とする低
温発生器４ならびに凝縮器５より成る発生凝縮
器、６は蒸発器７および吸収器８より成る蒸発吸
収器、９，１０，１１はそれぞれ溶液熱交換器、
低温溶液熱交換器、高温溶液熱交換器、P1は吸
収器８から低温溶液熱交換器１０、高温溶液熱交
換器１１経由で高温発生器１へ吸収液を送る高揚
程の第１ポンプ、P2は吸収器８から溶液熱交換
器９経由で低温熱源用発生器３へ吸収液を送る低
揚程の第２ポンプ、Ｐは冷媒液用のポンプであ
る。(F) Embodiment The drawing is a schematic configuration diagram showing an embodiment of this type of absorption refrigerator according to the present invention, in which 1 is a high temperature generator using high temperature combustion waste gas as a heat source, 2 is an engine cooling water In other words, the generation condenser 6 is composed of a low temperature heat source generator 3 whose heat source is low temperature hot water flowing out of the engine jacket, a low temperature generator 4 whose heat source is the refrigerant from the high temperature generator 1, and a condenser 5. An evaporator-absorber consisting of an evaporator 7 and an absorber 8; 9, 10, and 11 are each a solution heat exchanger;
A low-temperature solution heat exchanger, a high-temperature solution heat exchanger, P 1 is a high-lift first pump that sends the absorption liquid from the absorber 8 to the high-temperature generator 1 via the low-temperature solution heat exchanger 10 and the high-temperature solution heat exchanger 11; P 2 is a second pump with a low lift that sends the absorption liquid from the absorber 8 to the low-temperature heat source generator 3 via the solution heat exchanger 9, and P is a pump for refrigerant liquid.
そして、高温発生器１、発生凝縮器２、蒸発吸
収器６、低温溶液熱交換器１０、高温溶液熱交換
器１１、第１ポンプP1およびポンプＰを冷媒の
流れる管１２，１３、冷媒液の流下する管１４、
冷媒液の還流する管１５，１６で結んで冷媒の循
環路を形成すると共に吸収液の送られる管１７，
１８，１９，２０、吸収液の流れる管２１，２
２、吸収液の流れる管２４，２５，２６、で結ん
で吸収液の循環路を形成し、二重効用の吸収冷凍
サイクルが構成されるようになつている。 The high temperature generator 1, the generation condenser 2, the evaporator absorber 6, the low temperature solution heat exchanger 10, the high temperature solution heat exchanger 11, the first pump P1 and the pump P are connected to pipes 12 and 13 through which the refrigerant flows, and the refrigerant liquid a pipe 14 flowing down,
A pipe 17, which is connected by pipes 15 and 16 through which the refrigerant liquid returns to form a refrigerant circulation path, and through which the absorption liquid is sent;
18, 19, 20, pipes 21, 2 through which absorption liquid flows
2. The pipes 24, 25, and 26 through which the absorption liquid flows are connected to form a circulation path for the absorption liquid, thereby constructing a dual-effect absorption refrigeration cycle.
また、発生凝縮器２、蒸発吸収器６、溶液熱交
換器９、第２ポンプP2およびポンプＰを管１４，
１５，１６で結んで冷媒の循環路を形成すると共
に吸収液の送られる管２７，２８，２９、吸収液
の流れる管３０，３１，２６を結んで前述の吸収
液の循環路〔二重効用の吸収冷凍サイクル側の循
環路〕に並列な吸収液の循環路を形成し、一重効
用の吸収冷凍サイクルが構成されるようになつて
いる。 In addition, the generation condenser 2, the evaporator absorber 6, the solution heat exchanger 9, the second pump P2 , and the pump P are connected to the pipe 14,
15 and 16 to form a refrigerant circulation path, and the absorption liquid flow pipes 27, 28, 29, and absorption liquid flow tubes 30, 31, and 26 are connected to form the above-mentioned absorption liquid circulation path [double effect]. A parallel circulation path for the absorption liquid is formed in the absorption refrigeration cycle side of the absorption refrigeration cycle, thereby constructing a single-effect absorption refrigeration cycle.
３２，３２……は高温発生器１に配備された高
温の廃ガスの流れる加熱管、３３は低温発生器４
に内蔵された給熱器、３４は低温熱源用発生器３
に内蔵された加熱器、３５は蒸発器７に内蔵され
た給水器、３６，３７はそれぞれ凝縮器５、吸収
器８に内蔵した冷却器である。 32, 32... are heating pipes through which high-temperature waste gas flows, which are installed in the high-temperature generator 1, and 33 is the low-temperature generator 4.
34 is a low-temperature heat source generator 3.
35 is a water supply device built into the evaporator 7, and 36 and 37 are coolers built into the condenser 5 and absorber 8, respectively.
３８は発電プラントなどの設備に用いられてい
るエンジンで、このエンジンの燃焼廃ガス出口と
高温発生器１の加熱管３２，３２……がダクト３
９で結ばれている。そして、４０は高温発生器１
からの廃ガスの排出用ダクトで、このダクトを介
して高温発生器１内の吸収液を加熱した後の廃ガ
スが大気中へ放出される。また、エンジン３８の
ジヤケツト〔図示せず〕と低温熱源用発生器３の
加熱器３４とが管４１およびポンプP0付きの管
４２で結ばれて温水の循環路が形成されている。
なお、４３，４４は冷水器３５と負荷側熱交換ユ
ニツト〔図示せず〕を結んだ冷水用の管であり、
４５，４６，４７は冷却器３７，３６を直列に結
んだ冷却水用の管である。 38 is an engine used in equipment such as a power generation plant, and the combustion waste gas outlet of this engine and the heating pipes 32, 32, . . . of the high temperature generator 1 are connected to the duct 3.
They are connected by 9. And 40 is high temperature generator 1
A duct for discharging waste gas from the high temperature generator 1, through which the waste gas after heating the absorption liquid in the high temperature generator 1 is discharged into the atmosphere. Further, a jacket (not shown) of the engine 38 and the heater 34 of the low-temperature heat source generator 3 are connected by a pipe 41 and a pipe 42 with a pump P 0 to form a hot water circulation path.
Note that 43 and 44 are cold water pipes connecting the water cooler 35 and the load-side heat exchange unit (not shown).
45, 46, 47 are cooling water pipes connecting the coolers 37, 36 in series.
ST1は高温発生器１内の吸収液の温度を感知す
る検出器、SP1は高温発生器１内の圧力を感知す
る検出器、S1は廃ガスの排出用ダクト４０内の温
度を感知する検出器で、これら検出器のいずれか
の信号により第１制御器C1を介して第１ポンプ
P1の吐出量または管２９に備えた流量制御弁V2
の開度が調節されるようになつている。また、
ST2は低温熱源用発生器３内の吸収液の温度を感
知する検出器、SP2は発生凝縮器２内の圧力を感
知する検出器、S2は管４１内の温水の温度を感知
する検出器で、これら検出器のいずれかの信号に
より第２制御器C2を介して第２ポンプP2の吐出
量または管１８に備えた流量制御弁V1の開度が
調節されるようになつている。なお、図示してい
ないが第１制御器C1を介して第２ポンプP2が制
御され、第２制御器C2を介して第１ポンプP1が
制御されるよう構成しても良い。なおまた、第１
制御器C1を介して管１８に備えた流量制御弁V1
の開度が調節され、第２制御器C2を介して管２
９に備えた流量制御弁V2の開度が調節されるよ
うに構成しても良い。 S T1 is a detector that senses the temperature of the absorption liquid inside the high temperature generator 1, S P1 is a detector that senses the pressure inside the high temperature generator 1, and S 1 is a detector that senses the temperature inside the waste gas discharge duct 40. A signal from one of these detectors causes the first pump to be activated via the first controller C1 .
Discharge volume of P 1 or flow control valve V 2 provided in pipe 29
The opening degree can be adjusted. Also,
S T2 is a detector that senses the temperature of the absorption liquid in the low-temperature heat source generator 3, S P2 is a detector that senses the pressure in the generation condenser 2, and S 2 is a detector that senses the temperature of hot water in the pipe 41. With the detector, the discharge amount of the second pump P 2 or the opening degree of the flow control valve V 1 provided in the pipe 18 is adjusted via the second controller C 2 based on the signal from one of these detectors. It's summery. Although not shown, the second pump P2 may be controlled via the first controller C1, and the first pump P1 may be controlled via the second controller C2 . Furthermore, the first
Flow control valve V 1 provided in pipe 18 via controller C 1
The opening degree of pipe 2 is adjusted via the second controller C2.
The opening degree of the flow rate control valve V2 provided at 9 may be adjusted.
次に、このように構成されたこの種の吸収冷凍
機（以下、本機という）の動作例を説明する。 Next, an example of the operation of this type of absorption refrigerating machine (hereinafter referred to as the present machine) configured as described above will be explained.
今、本機の運転中にエンジン３８側の負荷〔例
えば電力需要〕が減りこれに合わせてエンジン３
８の動力を弱める制御がなされた場合、エンジン
３８の発熱量が減少してそのジヤケツトから低温
熱源用発生器３へ供給される温水およびエンジン
３８から高温発生器１へ供給される燃焼廃ガスの
エンタルピーが小さくなるため、これら発生器
１，３での冷媒蒸気の発生量が減り始め、高温発
生器１および発生凝縮器２内の蒸気圧が降下し始
めると共にこれら発生器内の吸収液の温度も降下
し始める。 Now, while the machine is operating, the load on the engine 38 side (for example, electricity demand) decreases and the engine 38
8, the calorific value of the engine 38 decreases, and the hot water supplied from the jacket to the low-temperature heat source generator 3 and the combustion waste gas supplied from the engine 38 to the high-temperature generator 1 decrease. Since the enthalpy becomes smaller, the amount of refrigerant vapor generated in these generators 1 and 3 begins to decrease, and the vapor pressure in the high temperature generator 1 and generation condenser 2 begins to decrease, and the temperature of the absorption liquid in these generators decreases. also begins to fall.
そして、これをそのまま放置すると吸収液の濃
縮〔冷媒蒸気の発生〕が十分なされずに本機の運
転効率（冷凍効率）の悪化を引起こすと同時に管
４１内の温水の温度すなわちエンジン３８のジヤ
ケツトへの温水の戻り温度も低くなつてエンジン
３８の冷え過ぎを引起こす。 If this is left as it is, the absorption liquid will not be sufficiently concentrated (refrigerant vapor generated), causing deterioration of the operating efficiency (refrigeration efficiency) of the machine, and at the same time, the temperature of the hot water in the pipe 41, that is, the jacket of the engine 38, will decrease. The temperature of the hot water returned to the engine also becomes low, causing the engine 38 to become too cold.
このような場合、本機においては、検出器ST1，
SP1，S1のいずれかの信号で第１制御器C1を介し
て第１ポンプP1の吐出量または検出器ST2，SP2，
S2のいずれかの信号で第２制御器C2を介して流
量制御弁V1の開度を減じることにより高温発生
器１への吸収液の送り量が減らされると共に、検
出器ST2，SP2，S2のいずれかの信号で第２制御器
C2を介して第２ポンプP2の吐出量または検出器
ST1，SP1，S1のいずれかの信号で第１制御器C1を
介して流量制御弁V2の開度を減じることにより
低温熱源用発生器３への吸収液の送り量が減らさ
れる。その結果、高温発生器１および低温熱源用
発生器３内の吸収液の顕熱消費量〔吸収液を沸騰
温度まで昇温させるのに必要な熱量〕が少なくな
り、その分、燃焼廃ガスおよび温水の熱の多くが
吸収液から冷媒を分離させる〔吸収液を濃縮す
る〕のに消費（以下、潜熱消費という）されるこ
とになる。このため、本機においては、良好に冷
媒蒸気を発生させて吸収液を濃縮することがで
き、運転効率の低下を防ぐことができる。かつま
た、低温熱源用発生器３での吸収液の濃縮の度合
すなわち濃度をエンジン３８の動力の弱められる
以前と同程度まで復帰させることも可能となる。
このように、低温熱源用発生器３内の吸収液の濃
度をほぼ一定の範囲内に保つことによつて、その
飽和蒸気圧および飽和温度〔沸騰温度〕すなわち
低温熱源用発生器３内の吸収液温度をほぼ一定の
範囲内に保ち得るので、この発生器から流出する
温水言い代えればエンジン３８のジヤケツトへ戻
る温水〔エンジン用冷却水〕の温度をほぼ所定の
範囲内に維持できる。したがつて、エンジン３８
の冷え過ぎを引起こすようなこともない。 In such a case, this machine uses detectors S T1 ,
The discharge amount of the first pump P1 or the detector S T2 , S P2 ,
By reducing the opening degree of the flow rate control valve V 1 via the second controller C 2 in response to any signal from S 2 , the amount of absorption liquid sent to the high temperature generator 1 is reduced, and the amount of absorption liquid sent to the high temperature generator 1 is reduced. The second controller is activated by either S P2 or S 2 signal.
Discharge rate or detector of second pump P 2 via C 2
The amount of absorption liquid sent to the low temperature heat source generator 3 is reduced by reducing the opening degree of the flow rate control valve V 2 via the first controller C 1 using any of the signals S T1 , S P1 , and S 1 . It can be done. As a result, the sensible heat consumption of the absorption liquid in the high-temperature generator 1 and the low-temperature heat source generator 3 (the amount of heat required to raise the temperature of the absorption liquid to boiling temperature) decreases, and the amount of combustion waste gas and Much of the heat of the hot water is consumed (hereinafter referred to as latent heat consumption) in separating the refrigerant from the absorption liquid (concentrating the absorption liquid). Therefore, in this machine, refrigerant vapor can be generated well to concentrate the absorption liquid, and a decrease in operating efficiency can be prevented. Moreover, it is also possible to restore the degree of concentration, that is, the concentration, of the absorption liquid in the low-temperature heat source generator 3 to the same level as before the power of the engine 38 was weakened.
In this way, by keeping the concentration of the absorption liquid in the generator 3 for low-temperature heat source within a substantially constant range, the saturated vapor pressure and the saturated temperature (boiling temperature), that is, the absorption liquid in the generator 3 for low-temperature heat source, can be reduced. Since the liquid temperature can be maintained within a substantially constant range, the temperature of the hot water flowing out from the generator, in other words, the hot water (engine cooling water) returning to the jacket of the engine 38, can be maintained within a substantially predetermined range. Therefore, engine 38
It will not cause your body to get too cold.
そして、逆にエンジン３８の動力が強められた
場合には高温発生器１および低温熱源用発生器３
への吸収液の送り量を増やすよう制御することに
より、燃焼廃ガスおよび温水のエンタルピーの増
大に応じて吸収液の顕熱消費量を調整しつつ燃焼
廃ガスおよび温水の熱量に対する吸収液の潜熱消
費量の割合をエンジン３８の動力の強められる以
前と同程度にすることが可能となる。このため、
低温熱源用発生器３内の吸収液温をほぼ所定の範
囲内に保つことができ、この発生器から流出する
温水の過度の温度上昇を防いでエンジン３８の過
熱を防ぐことができる。なお、エンジン３８の動
力変化の影響を受けて変化する物理量には吸収液
の濃度や冷媒蒸気の温度などもあるので、本機に
用いる検出器は図示したものに限定されない。 Conversely, when the power of the engine 38 is increased, the high temperature generator 1 and the low temperature heat source generator 3
By controlling the amount of absorption liquid fed to increase, the amount of latent heat of the absorption liquid relative to the calorific value of combustion waste gas and hot water is adjusted while adjusting the sensible heat consumption of the absorption liquid in accordance with the increase in enthalpy of combustion waste gas and hot water. It becomes possible to keep the consumption rate to the same level as before the power of the engine 38 was increased. For this reason,
The temperature of the absorption liquid in the low-temperature heat source generator 3 can be maintained within a substantially predetermined range, and the engine 38 can be prevented from overheating by preventing an excessive rise in temperature of the hot water flowing out from the generator. Note that the physical quantities that change under the influence of changes in the power of the engine 38 include the concentration of the absorbing liquid and the temperature of the refrigerant vapor, so the detector used in this device is not limited to the one shown in the figure.
また、本機においては、高揚程の第１ポンプ
P1の配備されている吸収液流路言い代えれば二
重効用の吸収冷凍サイクル側の吸収液の循環路と
低揚程の第２ポンプP2の配備されている吸収液
流路言い代えれば一重効用の吸収冷凍サイクル側
の吸収液の循環路とが並列に形成されているの
で、圧力変化の度合の異なる高温発生器１と低温
熱源用発生器３とを直列に結んでこれら発生器へ
吸収液をシリーズに送る従来のこの種の吸収冷凍
機のようにこれら発生器１，３での吸収液の出入
のバランスを保つための高揚程の第１ポンプP1
の吐出量制御と低揚程の第２ポンプP2の吐出量
制御との調整を必要とせず、これらポンプP1，
P2をそれぞれ独立に制御できる。このため、本
機は、従来のこの種の吸収冷凍機にくらべて、簡
便な制御で済むという利点をもつ。 In addition, in this machine, the first pump with high head
In other words, the absorption liquid flow path installed in P 1 is the double-effect absorption liquid circulation path on the absorption refrigeration cycle side, and the absorption liquid flow path installed in the second pump P 2 with low head is single-layered. Since the absorption liquid circulation path on the absorption refrigeration cycle side is formed in parallel, the high temperature generator 1 and the low temperature heat source generator 3, which have different degrees of pressure change, are connected in series and the absorption liquid is absorbed into these generators. Like this type of conventional absorption refrigerator that sends liquid in series, a high-head first pump P1 is used to maintain the balance of the absorption liquid in and out of these generators 1 and 3.
These pumps P 1 ,
P 2 can be controlled independently. Therefore, this machine has the advantage of requiring simpler control than conventional absorption refrigerators of this type.
(ト) 発明の効果
以上のとおり、本発明によれば、エンジン側の
動力が弱められた場合にこの種の吸収冷凍機の運
転効率の低下を簡便に軽減できる効果がもたらさ
れ、かつ、エンジンの動力の変動に対してこの種
の吸収冷凍機の低温熱源用発生器から流出する温
水言い代えればエンジン側へ戻る温水〔エンジン
用冷却水〕の温度変動を簡便な制御で小さくして
エンジンの冷え過ぎや過熱を防ぐ効果がもたらさ
れる。(G) Effects of the Invention As described above, the present invention provides an effect of easily reducing the decrease in operating efficiency of this type of absorption chiller when the power on the engine side is weakened, and In response to fluctuations in engine power, the temperature fluctuations of the hot water flowing out from the low-temperature heat source generator of this type of absorption refrigerator (in other words, the hot water [engine cooling water]) returning to the engine side can be reduced by simple control. This has the effect of preventing the water from becoming too cold or overheating.
図面は本発明によるこの種の吸収冷凍機の一実
施例を示した概略構成説明図である。
１……高温発生器、２……発生凝縮器、３……
低温熱源用発生器、４……低温発生器、５……凝
縮器、６……蒸発吸収器、７……蒸発器、８……
吸収器、９……溶液熱交換器、１０，１１……低
温、高温溶液熱交換器、１７〜３１……管、３２
……加熱管、３３……給熱器、３４……加熱器、
３５……冷水器、３６，３７……冷却器、３８…
…エンジン、３９，４０……ダクト、４１，４２
……管、C1，C2……第１、第２制御器、S1，S2，
ST1，ST2，SP1，SP2……検出器、P0，P1，P2……
ポンプ、V1，V2……流量制御弁。
The drawing is a schematic structural diagram showing an embodiment of this type of absorption refrigerator according to the present invention. 1... High temperature generator, 2... Generation condenser, 3...
Generator for low temperature heat source, 4... Low temperature generator, 5... Condenser, 6... Evaporative absorber, 7... Evaporator, 8...
Absorber, 9... Solution heat exchanger, 10, 11... Low temperature, high temperature solution heat exchanger, 17-31... Tube, 32
... heating tube, 33 ... heat supply device, 34 ... heater,
35... Water cooler, 36, 37... Cooler, 38...
...Engine, 39,40...Duct, 41,42
...Pipe, C 1 , C 2 ...First and second controllers, S 1 , S 2 ,
S T1 , S T2 , S P1 , S P2 ... Detector, P 0 , P 1 , P 2 ...
Pump, V 1 , V 2 ...flow control valve.
Claims (1)
として用いられる低温熱源用発生器、溶液熱交換
器および吸収器を結ぶ吸収液の循環路とエンジン
の廃ガスが熱源として用いられる高温発生器、こ
の高温発生器で吸収液から分離した冷媒が熱源と
して用いられる低温発生器、溶液熱交換器および
吸収器を結ぶ吸収液の循環路とが並列に形成さ
れ、かつ、高温発生器や低温熱源用発生器内の液
温や蒸気圧などこれら発生器に関連する物理量を
検知しつつ吸収器から高温発生器へ送る吸収液の
流量を調節する制御装置と吸収器から低温熱源用
発生器へ送る吸収液の流量を調節する制御装置と
が備えられて成ることを特徴とした一重二重効用
吸収冷凍機。1. A low-temperature heat source generator in which hot water circulating through the engine jacket is used as a heat source, an absorption liquid circulation path connecting the solution heat exchanger and absorber, and a high-temperature generator in which engine waste gas is used as a heat source. A low-temperature generator in which the refrigerant separated from the absorption liquid is used as a heat source, a solution heat exchanger, and an absorption liquid circulation path connecting the absorber are formed in parallel, and a high-temperature generator and a low-temperature heat source generator are formed in parallel. A control device that adjusts the flow rate of the absorption liquid sent from the absorber to the high-temperature generator while detecting physical quantities related to these generators, such as liquid temperature and vapor pressure, and a control device that adjusts the flow rate of the absorption liquid sent from the absorber to the low-temperature heat source generator. A single/double effect absorption refrigerating machine characterized by comprising: a control device for adjusting the temperature;
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15103085A JPS6213968A (en) | 1985-07-09 | 1985-07-09 | Single double effect absorption refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15103085A JPS6213968A (en) | 1985-07-09 | 1985-07-09 | Single double effect absorption refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6213968A JPS6213968A (en) | 1987-01-22 |
| JPH0583828B2 true JPH0583828B2 (en) | 1993-11-29 |
Family
ID=15509764
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15103085A Granted JPS6213968A (en) | 1985-07-09 | 1985-07-09 | Single double effect absorption refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6213968A (en) |
-
1985
- 1985-07-09 JP JP15103085A patent/JPS6213968A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6213968A (en) | 1987-01-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |