JPH0583829B2 - - Google Patents
Info
- Publication number
- JPH0583829B2 JPH0583829B2 JP15273685A JP15273685A JPH0583829B2 JP H0583829 B2 JPH0583829 B2 JP H0583829B2 JP 15273685 A JP15273685 A JP 15273685A JP 15273685 A JP15273685 A JP 15273685A JP H0583829 B2 JPH0583829 B2 JP H0583829B2
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- generator
- low
- absorption liquid
- heat source
- 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 77
- 239000007788 liquid Substances 0.000 claims description 70
- 239000006096 absorbing agent Substances 0.000 claims description 21
- 239000003507 refrigerant Substances 0.000 claims description 21
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 20
- 239000002912 waste gas Substances 0.000 claims description 11
- 230000000694 effects Effects 0.000 claims description 9
- 230000002745 absorbent Effects 0.000 claims description 3
- 239000002250 absorbent Substances 0.000 claims description 3
- 230000032258 transport Effects 0.000 claims 1
- 239000000243 solution Substances 0.000 description 12
- 230000007423 decrease Effects 0.000 description 11
- 239000000498 cooling water Substances 0.000 description 5
- 238000010438 heat treatment Methods 0.000 description 4
- 238000013021 overheating Methods 0.000 description 4
- 238000009835 boiling Methods 0.000 description 3
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 230000001276 controlling effect Effects 0.000 description 2
- 230000006866 deterioration Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- AMXOYNBUYSYVKV-UHFFFAOYSA-M lithium bromide Chemical compound [Li+].[Br-] AMXOYNBUYSYVKV-UHFFFAOYSA-M 0.000 description 2
- 229920006395 saturated elastomer Polymers 0.000 description 2
- 230000002411 adverse Effects 0.000 description 1
- 239000007864 aqueous solution Substances 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 238000010248 power generation Methods 0.000 description 1
- 230000001105 regulatory effect Effects 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）の改良に関する。[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が熱源に用いられる低温
熱源用発生器、溶液熱交換器および吸収器ならび
に低揚程の吸収液用ポンプを結んだ吸収液の循環
路と、エンジンの廃ガスが熱源に用いられる高温
発生器、低温発生器、低温溶液熱交換器、高温溶
液熱交換器および吸収器ならびに高揚程の吸収液
用ポンプを結んだ吸収液の循環路とを並列に形成
した一重二重効用吸収冷凍機が知られている。ま
た、この種の吸収冷凍機の他の従来の技術とし
て、例えば、特開昭58−85073号公報にみられる
ように、低温熱源用発生器、低温溶液熱交換器お
よび吸収器ならびにこの吸収器から低温熱源用発
生器へ吸収液を送るための低揚程ポンプを結ぶ吸
収液の循環路と、高温発生器、高温溶液熱交換
器、低温発生器、低温溶液熱交換器、吸収器、低
揚程ポンプおよび低温熱源用発生器ならびにこの
発生器から高温発生器へ吸収液を送るための高揚
程ポンプを結ぶ吸収液の循環路とを形成した一重
二重効用吸収冷凍機が知られている。(b) Conventional technology Conventional technology for this type of absorption refrigerator includes a low-temperature heat source generator that uses engine jacket hot water as a heat source, and a solution heat An absorption liquid circulation path connecting exchangers, absorbers, and low-head absorption liquid pumps, and high-temperature generators, low-temperature generators, low-temperature solution heat exchangers, and high-temperature solution heat exchangers that use engine waste gas as a heat source. A single-double effect absorption refrigerator is known in which an absorber, an absorber, and an absorption liquid circulation path connecting a high-head absorption liquid pump are formed in parallel. Other conventional techniques for this type of absorption refrigerator include, for example, a generator for a low temperature heat source, a low temperature solution heat exchanger and an absorber, and the absorber An absorption liquid circulation path connecting a low head pump for sending absorption liquid from the to the low temperature heat source generator, a high temperature generator, a high temperature solution heat exchanger, a low temperature generator, a low temperature solution heat exchanger, an absorber, and a low head pump. A single-double effect absorption refrigerator is known which includes a pump, a generator for a low-temperature heat source, and an absorption liquid circulation path connecting a high-head pump for sending absorption liquid from the generator to a high-temperature generator.
(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悪化す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側へ戻る冷却水の温度が過度
に低くなつてエンジンの冷え過ぎを引起こす問題
点もある。なお、逆の場合には、エンジンの過熱
を引起こすおそれもある。(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. 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.
As a result, the temperature of the hot water flowing out from the low-temperature heat source generator, or in other words, the temperature of the cooling water returning to the engine, becomes excessively low, causing the engine to become too cold. Note that in the opposite case, there is a risk that the engine will overheat.
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、この種の吸収冷凍機の低温熱源用発生器、溶
液熱交換器および吸収器ならびに低揚程ポンプを
結ぶ吸収液の循環路と高温発生器、低温発生器、
溶液熱交換器および吸収器ならびに低揚程ポンプ
より吐出された吸収液を高温発生器側へ送る高揚
程ポンプを結ぶ吸収液の循環路とを形成し、か
つ、低温熱源用発生器や高温発生器内の液温、蒸
気圧などこれら発生器に関連する物理量を検知し
つつ吸収器側から低温熱源用発生器側への吸収液
流量を調節すると共に吸収器側から高温発生器側
への吸収液流量を調節する制御装置を備える構成
としたものである。(d) Means for solving the problems As a means for solving the above problems, the present invention provides a low-temperature heat source generator, a solution heat exchanger and an absorber, and a low-head pump for this type of absorption refrigerator. The absorption liquid circulation path that connects the high temperature generator, low temperature generator,
Forms an absorption liquid circulation path that connects the solution heat exchanger, the absorber, and the high head pump that sends the absorption liquid discharged from the low head pump to the high temperature generator side, and also connects the low head heat source generator and the high temperature generator. While detecting the physical quantities related to these generators, such as the liquid temperature and vapor pressure inside, the flow rate of the absorption liquid from the absorber side to the low temperature heat source generator side is adjusted, and the absorption liquid flow from the absorber side to the high temperature generator side is adjusted. This configuration includes a control device that adjusts the flow rate.
(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.
(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
燃焼廃ガスを熱源に用いて吸収液より冷媒を分離
する高温発生器、２は高温発生器１で分離された
冷媒を熱源に用いて吸収液より冷媒を分離する低
温発生器３とエンジン冷却用循環水言い代えれば
エンジンジヤケツトからの低温の温水を熱源に用
いて吸収液より冷媒を分離する低温熱源用発生器
４と凝縮器５とで成る発生凝縮器、６は蒸発器７
と吸収器８とで成る蒸発吸収器、９，１０はそれ
ぞれ低温、高温溶液熱交換器、PRは冷媒液用の
ポンプ、PLは吸収器８から低温熱源用発生器４
へ吸収液を送るための低揚程ポンプ、PHは低揚
程ポンプPLより吐出された吸収液を高温発生器
１へ送るための高揚程ポンプである。(F) Embodiment The drawing is a schematic structural explanatory diagram showing an embodiment of this type of absorption refrigerator according to the present invention. A generator 2 uses the refrigerant separated by the high-temperature generator 1 as a heat source to separate the refrigerant from the absorption liquid. A low-temperature generator 3 separates the refrigerant from the absorption liquid. A generation condenser consisting of a low-temperature heat source generator 4 and a condenser 5 for separating the refrigerant from the absorption liquid using the evaporator 7;
9 and 10 are low-temperature and high-temperature solution heat exchangers, respectively, P R is a pump for refrigerant liquid, and P L is a generator 4 for low-temperature heat source from absorber 8.
A low head pump P H is a high head pump that sends the absorbent discharged from the low head pump PL to the high temperature generator 1.
そして、発生凝縮器２、蒸発吸収器６、低温溶
液熱交換器９、冷媒液用のポンプPR、吸収液用
の低揚程ポンプPLを冷媒液の流下する管１１、
冷媒液の還流する管１２，１３、吸収液の送られ
る管１４，１５，１６，１７、吸収液の流れる管
１８，１９により接続して冷媒〔水〕と吸収液
〔臭化リチウム水溶液〕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。 The generation condenser 2, the evaporator absorber 6, the low-temperature solution heat exchanger 9, the refrigerant liquid pump PR , and the absorption liquid low head pump PL are connected to a pipe 11 through which the refrigerant liquid flows,
The refrigerant [water] and the absorption liquid [lithium bromide aqueous solution] are connected by pipes 12 and 13 through which the refrigerant liquid returns, pipes 14, 15, 16, and 17 through which the absorption liquid is sent, and pipes 18 and 19 through which the absorption liquid flows. A circulation path is formed to constitute a single-effect absorption refrigeration cycle.
また、高温発生器１、発生凝縮器２、蒸発吸収
器６、低温、高温溶液熱交換器９，１０、冷媒液
用のポンプPR、吸収液用の低揚程ポンプPLおよ
び高揚程ポンプPHを冷媒の流れる管２０，２１、
前記の冷媒液用管１１，１２，１３、前記の吸収
液用の管１４，１５，１６、吸収液の送られる管
２２，２３，２４、吸収液の流れる管２５，２
６、吸収液の流下する管２７、前記の吸収液用管
１８，１９により接続して冷媒と吸収液の循環路
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。 Also, high temperature generator 1, generation condenser 2, evaporator absorber 6, low temperature and high temperature solution heat exchangers 9 and 10, pump P R for refrigerant liquid, low head pump PL and high head pump P for absorption liquid. H is a refrigerant flowing pipe 20, 21,
The refrigerant liquid pipes 11, 12, 13, the absorption liquid pipes 14, 15, 16, the absorption liquid pipes 22, 23, 24, and the absorption liquid flow pipes 25, 2.
6. A pipe 27 through which the absorption liquid flows is connected by the absorption liquid pipes 18 and 19 to form a circulation path for the refrigerant and absorption liquid, and a dual-effect absorption refrigeration cycle is constructed. .
２８，２８……は高温発生器１に配備された加
熱管、２９は低温発生器３に内蔵された給熱器、
３０は低温熱源用発生器４に内蔵された加熱器、
３１は蒸発器７に内蔵された冷水器、３２，３３
はそれぞれ凝縮器５、吸収器８に内蔵された冷却
器である。 28, 28... are heating tubes installed in the high temperature generator 1, 29 is a heat feeder built in the low temperature generator 3,
30 is a heater built into the low temperature heat source generator 4;
31 is a water cooler built into the evaporator 7, 32, 33
are coolers built into the condenser 5 and absorber 8, respectively.
３４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２８，２８……がダクト３
５で結ばれている。そして、３６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
して廃ガスが大気中へ放出される。また、エンジ
ン３４のジヤケツト〔図示せず〕と低温熱源用発
生器４の加熱器３０とが管３７およびポンプＰ付
きの管３８で結ばれて温水の循環路が形成されて
いる。なお、３９，４０は冷水器３１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、４１，４２，４３は冷却器３３，３２を直
列に結んだ冷却水用の管である。なお、Ｖは管１
７に備えた逆止弁である。 34 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 28, 28 of the high temperature generator 1 are connected to the duct 3.
They are connected by 5. 36 is a high temperature generator 1
A duct for discharging waste gases from the duct, through which the waste gases are discharged into the atmosphere. Further, a jacket (not shown) of the engine 34 and the heater 30 of the low-temperature heat source generator 4 are connected by a pipe 37 and a pipe 38 with a pump P to form a hot water circulation path. Note that 39 and 40 are cold water pipes that connect the water cooler 31 and the load-side heat exchange unit (not shown), and 41, 42, and 43 are cooling water pipes that connect the coolers 33 and 32 in series. It's a tube. In addition, V is tube 1
This is a check valve equipped with 7.
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３６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を介して高揚程ポン
プPHの吐出量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４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３７内の温水の温度
を感知する検出器であり、C2は検出器ST2，SP2，
S2のいずれかの信号を受けつつ制御信号を発する
第２制御器である。C0は第１，第２制御器C1，
C2からの制御信号を受けつつそのトータル制御
信号を発する調整器で、この調整器から発信され
るトータル制御信号により低揚程ポンプPLの吐
出量が調節されるようになつている。 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 36. The discharge amount of the high-head pump P H is adjusted by a signal from one of these detectors via the first controller C1 .
Further, S T2 is a detector that senses the temperature of the absorption liquid in the generator 4 for low-temperature heat source, 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 the hot water in the pipe 37. C 2 is a detector for sensing, and C 2 is a detector S T2 , S P2 ,
This is a second controller that issues a control signal while receiving one of the signals of S2 . C 0 is the first and second controller C 1 ,
This is a regulator that receives a control signal from C2 and issues a total control signal, and the discharge amount of the low head pump PL is adjusted by the total control signal issued from this regulator.
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３４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
４の動力を弱める制御がなされた場合、エンジン
３４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４へ供給される温水およびエンジン
３４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
１，４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。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３７内の温水言い代えればエンジン３４
のジヤケツトへ戻るエンジン用冷却水の温度も低
くなつてエンジン３４の冷え過ぎを引起こす。 Now, while the machine is operating, the load on the engine 34 side (for example, electricity demand) decreases, and the engine 3
When control is performed to weaken the power of the engine 34, the calorific value of the engine 34 decreases, and the hot water supplied from the jacket to the low-temperature heat source generator 4 and the combustion waste gas supplied from the engine 34 to the high-temperature generator 1 are reduced. As the enthalpy becomes smaller, the amount of refrigerant vapor generated in these generators 1 and 4 begins to decrease, the vapor pressure in the high temperature generator 1 and the generation condenser 2 begins to decrease, and the temperature of the absorption liquid in these generators decreases. also begins to fall. If this is left as it is, the absorption liquid will not be sufficiently concentrated (refrigerant vapor generation), causing a deterioration of the operating efficiency (refrigeration efficiency) of the machine, and at the same time, the hot water inside the pipe 37, in other words, the engine 34.
The temperature of the engine cooling water returning to the jacket also becomes low, causing the engine 34 to become too cold.
このような場合、本機においては、検出器ST1，
SP1，S1のいずれかの信号を受けつつ制御信号を
発する第１制御器C1により高揚程ポンプPHの吐
出量が減らされると共に、検出器ST2，SP2，S2の
いずれかの信号を受ける第２制御器C2の制御信
号と前記第１制御器C1の制御信号とのトータル
制御信号により調整器C0を介して低揚程ポンプ
PLの吐出量が減らされる。その結果、高温発生
器１および低温熱源用発生器４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４での吸
収液の濃縮の度合すなわち濃度をエンジン３４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
４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、飽和温度〔沸騰温
度〕すなわち低温熱源用発生器４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３４のジ
ヤケツトへ戻る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
３４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 high head pump P H is reduced by the first controller C 1 which issues a control signal while receiving a signal from one of the detectors S T2 , S P2 and S 2 . The low head pump is controlled via the regulator C0 by the total control signal of the control signal of the second controller C2 which receives the signal and the control signal of the first controller C1 .
The discharge amount of P L is reduced. As a result, the sensible heat consumption of the absorption liquid in the high-temperature generator 1 and the low-temperature heat source generator 4 (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. Furthermore, 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 4 to the same level as before the power of the engine 34 was weakened. In this way, by keeping the concentration of the absorption liquid in the generator 4 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 4 for low-temperature heat source, are Since the liquid temperature can be maintained within a substantially constant range, the temperature of the hot water flowing out from the generator, or in other words, the temperature of the engine cooling water returning to the jacket of the engine 34, can be maintained within a substantially predetermined range. Therefore, the engine 34 will not become too cold.
そして、逆にエンジン３４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４
への吸収液の送り量を増すよう制御することによ
り、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３４の動力の強め
られる以前と同程度に復帰させてこの種の吸収冷
凍機の負荷に見合う冷凍能力を発揮させることが
可能であると共にその運転効率をエンジン３４の
動力の強められる以前と同程度に保つことが可能
である。かつまた、低温熱源用発生器３４内の吸
収液温をほぼ所定の範囲内に保つことも可能であ
り、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３４の過熱を防止することが
できる。 Conversely, when the power of the engine 34 is increased, the high temperature generator 1 and the low temperature heat source generator 4
By controlling the amount of absorption liquid to be increased to It is possible to exhibit a refrigerating capacity commensurate with the load of the absorption refrigerating machine, and it is also possible to maintain its operating efficiency at the same level as before the power of the engine 34 was increased. Moreover, it is also possible to maintain the temperature of the absorbent liquid in the low-temperature heat source generator 34 within a predetermined range, thereby preventing an excessive temperature rise of the hot water flowing out from this generator and preventing the engine 34 from overheating. be able to.
また、本機においては、低揚程ポンプPLの吐
出量が第１制御器C1の制御信号で調節される高
揚程ポンプPHの吐出量の増減分を補なうように、
第１制御器C1からの制御信号も含めたトータル
制御信号〔第１制御器C1と第２制御器C2とのト
ータル制御信号〕で調節されるため、高揚程ポン
プPHへ送られる吸収液の量に過不足を生じるこ
ともない。このため、吸収液を良好に循環させる
ことができる。また、調整器C0を介在させずに
第１、第２制御器C1，C2の信号を直接に低揚程
ポンプPLへ送るよにしても良く、また、第１制
御器C1からの信号を高揚程ポンプPH経由で低揚
程ポンプPLへ送るようにしても良い。 In addition, in this machine, the discharge amount of the low head pump PL compensates for the increase/decrease in the discharge amount of the high head pump PH , which is adjusted by the control signal of the first controller C1 .
It is regulated by the total control signal including the control signal from the first controller C 1 [total control signal of the first controller C 1 and the second controller C 2 ], so it is sent to the high head pump P H There will be no excess or deficiency in the amount of absorption liquid. Therefore, the absorption liquid can be circulated well. Furthermore, the signals from the first and second controllers C 1 and C 2 may be sent directly to the low head pump P L without intervening the regulator C 0 , or the signals from the first controller C 1 may be sent directly to the low head pump P L without intervening the regulator C 0 . The signal may be sent to the low head pump P L via the high head pump P H.
なおまた、本機においては、ポンプPH，PLの
吐出量を調節する代りに、管２４〔あるいは、図
示していないが、管２２，２３など〕に備えた流
量制御弁V1の開度を第１制御器C1からの制御信
号で調節すると共に管１７に備えた流量制御弁
V2の開度を第２制御器C2からの制御信号で調節
するようにしても良い。あるいは、図示していな
いが、流量制御弁V1の開度を第２制御器C2の信
号で調節する一方流量制御弁V2の開度を第１制
御器C1の信号で調節することも可能である。流
量制御弁V1，V2の開度を調節することによつて
発生器１，４への吸収液の送り量を制御する場合
には、高揚程ポンプPHの吸込側圧力が変動して
このポンプの吐出量制御にやゝ悪影響を及ぼすも
のの、その程度は軽微であり、吸収液の循環に障
害を及ぼす程のものでもない。 Furthermore, in this machine, instead of adjusting the discharge amount of the pumps P H and P L , the flow rate control valve V 1 provided in the pipe 24 (or, although not shown, the pipes 22, 23, etc.) is opened. The flow rate control valve is provided in the pipe 17 and adjusts the temperature by a control signal from the first controller C1 .
The opening degree of V 2 may be adjusted by a control signal from the second controller C 2 . Alternatively, although not shown, the opening degree of the flow rate control valve V 1 may be adjusted using the signal from the second controller C 2 while the opening degree of the flow rate control valve V 2 may be adjusted using the signal from the first controller C 1 . is also possible. When controlling the amount of absorption liquid sent to the generators 1 and 4 by adjusting the opening degrees of the flow control valves V 1 and V 2 , the suction side pressure of the high head pump PH fluctuates. Although this has a slight adverse effect on the control of the discharge amount of the pump, the degree of the effect is slight and does not interfere with the circulation of the absorption liquid.
なお、ポンプPH，PLや流量制御弁V1，V2の制
御度合はこの種の吸収冷凍機の容量やエンジン３
４の容量などの仕様に応じて適宜選定される。 The degree of control of the pumps P H and P L and the flow control valves V 1 and V 2 depends on the capacity of this type of absorption refrigerator and the engine 3.
It is selected as appropriate depending on the specifications such as the capacity of No. 4.
なおまた、エンジン３４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。また、液温を感知す
る検出器は液中にセンサー部を浸す構造のもの以
外に管壁や器壁の温度を介して液温を間接的に検
知する構造のものであつても良い。 Furthermore, since physical quantities that change under the influence of changes in the power of the engine 34 include the concentration of the absorbing liquid and the temperature of the refrigerant vapor, the detector used in this device is not limited to the one shown. Further, the detector for sensing the liquid temperature may have a structure in which the sensor portion is immersed in the liquid, or may have a structure in which the liquid temperature is indirectly detected through the temperature of the tube wall or the container wall.
(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エンジン用冷却水の温
度変動を小さくし、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, according to the present invention, it is possible to reduce the decrease in operating efficiency of this type of absorption chiller when the power on the engine side is weakened, and also to improve the efficiency of the engine. In other words, the hot water that flows out from the low-temperature heat source generator of this type of absorption refrigerator in response to fluctuations in power reduces the temperature fluctuations of the engine cooling water that returns to the engine side, and has the effect of preventing the engine from becoming too cold or overheating. brought about.
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……
低温発生器、４……低温熱源用発生器、５……凝
縮器、６……蒸発吸収器、７……蒸発器、８……
吸収器、９，１０……低温、高温溶液熱交換器、
１４，１５，１６，１７，１８，１９……管、２
２，２３，２４，２５，２６，２７……管、２８
……加熱管、２９……給熱器、３０……加熱器、
３１……冷水器、３２，３３……冷却器、３４…
…エンジン、３５，３６……ダクト、３７，３８
……管、C1，C2……第１、第２制御器、C0……
調整器、PH……高揚程ポンプ、PL……低揚程ポ
ンプ、ST1，SP1，S1，ST2，SP2，S2……検出器、
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...
Low temperature generator, 4... Generator for low temperature heat source, 5... Condenser, 6... Evaporative absorber, 7... Evaporator, 8...
Absorber, 9, 10...low temperature, high temperature solution heat exchanger,
14, 15, 16, 17, 18, 19...tube, 2
2, 23, 24, 25, 26, 27... tube, 28
... heating tube, 29 ... heat supply device, 30 ... heater,
31... Water cooler, 32, 33... Cooler, 34...
...Engine, 35, 36...Duct, 37, 38
...Tube, C 1 , C 2 ... First and second controllers, C 0 ...
Regulator, P H ... High head pump, P L ... Low head pump, S T1 , S P1 , S 1 , S T2 , S P2 , S 2 ... Detector,
V 1 , V 2 ...Flow control valve.
Claims (1)
に用いられる低温熱源用発生器、溶液熱交換器お
よび吸収器ならびに吸収液を前記吸収器から低温
熱源用発生器へ送る低揚程のポンプを結ぶ吸収液
の循環路とエンジンの廃ガスが熱源に用いられる
高温発生器、この高温発生器で吸収液より分離さ
れた冷媒が熱源に用いられる低温発生器、溶液熱
交換器および前記吸収器ならびに低揚程の前記ポ
ンプより吐出された吸収液を高温発生器へ送る高
揚程のポンプを結ぶ吸収液の循環路とが形成さ
れ、かつ前記低温熱源用発生器や高温発生器内の
液温、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側から低温熱源用発生器側へ
の吸収液の流量を調節すると共に吸収器側から高
温発生器側への吸収液の流量を調節する制御装置
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, a solution heat exchanger, and an absorber in which hot water circulating through the engine jacket is used as a heat source, and a low-head pump that transports the absorbent liquid from the absorber to the low-temperature heat source generator. A high-temperature generator in which waste gas from the circulation path and the engine is used as a heat source, a low-temperature generator in which a refrigerant separated from an absorption liquid in this high-temperature generator is used as a heat source, a solution heat exchanger and the absorber, and a low-head An absorption liquid circulation path is formed that connects the high-head pump that sends the absorption liquid discharged from the pump to the high-temperature generator. A control device is provided that adjusts the flow rate of the absorption liquid from the absorber side to the low-temperature heat source generator side while detecting physical quantities related to the generator, and also adjusts the flow rate of the absorption liquid from the absorber side to the high-temperature generator side. A single and double effect absorption refrigerator.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15273685A JPS6213970A (en) | 1985-07-11 | 1985-07-11 | Single double effect absorption refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15273685A JPS6213970A (en) | 1985-07-11 | 1985-07-11 | Single double effect absorption refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6213970A JPS6213970A (en) | 1987-01-22 |
| JPH0583829B2 true JPH0583829B2 (en) | 1993-11-29 |
Family
ID=15547033
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15273685A Granted JPS6213970A (en) | 1985-07-11 | 1985-07-11 | Single double effect absorption refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6213970A (en) |
-
1985
- 1985-07-11 JP JP15273685A patent/JPS6213970A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6213970A (en) | 1987-01-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EXPY | Cancellation because of completion of term |