JPS594862A - Absorption type heat pump device - Google Patents
Absorption type heat pump deviceInfo
- Publication number
- JPS594862A JPS594862A JP57113509A JP11350982A JPS594862A JP S594862 A JPS594862 A JP S594862A JP 57113509 A JP57113509 A JP 57113509A JP 11350982 A JP11350982 A JP 11350982A JP S594862 A JPS594862 A JP S594862A
- Authority
- JP
- Japan
- Prior art keywords
- absorber
- heat pump
- pump device
- coolant
- temperature
- 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.)
- Pending
Links
Landscapes
- Sorption Type Refrigeration Machines (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は、吸収式サイクルを用いて冷房・暖房および給
湯に利用する吸収式ヒートポンプサイクルの吸収器の冷
却液量制御に関するものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to controlling the amount of coolant in an absorber of an absorption heat pump cycle that is used for cooling, heating, and hot water supply using an absorption cycle.
従来の吸収式ヒートポンプ装置の冷却液量制御について
説明を行なう。第１図は従来の吸収式ヒートポンプ装置
の構成を示すものである。第１図において、１は吸収器
である。吸収器１で冷媒濃度が増加した溶液は溶液ポン
プ２で加圧され、溶液熱交換器３で加温される。その後
、発生器４で外部より加熱され冷媒蒸気を発生する。冷
媒発生により冷媒濃度が減少した溶液は、溶液熱交換器
３をとおり冷却され吸収器１へもどる。一方前記発生冷
媒は凝縮器５で液化し、膨張弁６で減圧後蒸発器了で蒸
発気化し吸収器１へもどる。吸収器１では冷媒潜熱と吸
収熱を除去するため冷却液が流れている。前記冷却水は
ポンプ９により加圧され吸収器１に入る。吸収器１で前
述のように昇温さね、その後放熱器（または貯湯槽）８
で放熱（または貯湯）されてポンプ９にもどる。前記冷
却液の流量は、流量調節弁１ｏにより制御される。Coolant amount control in a conventional absorption heat pump device will be explained. FIG. 1 shows the configuration of a conventional absorption heat pump device. In FIG. 1, 1 is an absorber. The solution whose refrigerant concentration has increased in the absorber 1 is pressurized by a solution pump 2 and heated by a solution heat exchanger 3. Thereafter, the generator 4 heats the refrigerant from the outside to generate refrigerant vapor. The solution whose refrigerant concentration has decreased due to refrigerant generation passes through the solution heat exchanger 3 and is cooled and returns to the absorber 1. On the other hand, the generated refrigerant is liquefied in the condenser 5, reduced in pressure by the expansion valve 6, evaporated in the evaporator, and returned to the absorber 1. In the absorber 1, a cooling liquid flows in order to remove latent heat of the refrigerant and absorbed heat. The cooling water is pressurized by a pump 9 and enters the absorber 1 . The temperature is raised in the absorber 1 as described above, and then the radiator (or hot water storage tank) 8
The heat is radiated (or stored) and returned to the pump 9. The flow rate of the cooling liquid is controlled by a flow rate control valve 1o.
これは吸収式ザイクルの起動時や負荷変動に対して、ザ
イクルが変化しすぎないようにするだめのものである。This is to prevent the cycle from changing too much when the absorption cycle is started or when the load changes.
例えば、起動時には蒸発器７から吸収器１へ流れる冷媒
ガスが少ないため発生する熱も少ない。また、冷房負荷
が減少すると蒸発器７で蒸発する冷媒量も減少し、起動
時と同様に吸収器１で発生する熱量は減少する。従って
、冷却液量を一定に保つと低圧が下がり蒸発温度が下降
する。この時、リチウムブロマイドを用いた吸収式シス
テムでは水の凍結を生ずる。まだ他の媒体を用いたシス
テムでも、蒸発器に着霜を起こしたり、高低圧差の増大
から成績係数の低下を生ずる。For example, at startup, less refrigerant gas flows from the evaporator 7 to the absorber 1, so less heat is generated. Further, when the cooling load decreases, the amount of refrigerant evaporated in the evaporator 7 also decreases, and the amount of heat generated in the absorber 1 decreases, as in the case of startup. Therefore, when the amount of coolant is kept constant, the low pressure decreases and the evaporation temperature decreases. At this time, water freezes in absorption systems using lithium bromide. Even in systems using other media, frost builds up on the evaporator and the coefficient of performance decreases due to an increase in the difference between high and low pressures.
このような現象を緩和するため、従来法のような制御が
とられている。起動時の現象に関しては、ポンプ９を作
動させない。つまり冷却液を流さずに吸収器１の温度が
一定温度に上昇した後にポンプ９を作動させる。またタ
イマーを用い始動後一定時間ポンプ９を作動させない等
の制御がなされている。一方、負荷側の変動に対しては
冷房負荷が低下すると蒸発器入口水温（または入口空気
温）が下がるので、この温度を検知して流量調節弁１゜
の開度を絞る。In order to alleviate this phenomenon, controls similar to conventional methods are taken. Regarding the phenomenon at startup, the pump 9 is not operated. That is, the pump 9 is operated after the temperature of the absorber 1 rises to a constant temperature without flowing the cooling liquid. Further, a timer is used to control the pump 9 such that it is not operated for a certain period of time after starting. On the other hand, regarding fluctuations on the load side, when the cooling load decreases, the evaporator inlet water temperature (or inlet air temperature) decreases, so this temperature is detected and the opening degree of the flow rate control valve 1° is reduced.
しかしながら、上記のような構成ではポンプ９と流量調
節弁１ｏなる２つの制御機構が必要となる。また、夏期
と冬期では、前記冷却液の吸収器１の入口温度が変化す
るため、吸収器１の出口温度は夏期に高く冬期に低いも
のになる。これは冬期の出湯温度か下がるという欠点を
有している。However, the above configuration requires two control mechanisms: the pump 9 and the flow control valve 1o. Moreover, since the inlet temperature of the coolant to the absorber 1 changes between summer and winter, the outlet temperature of the absorber 1 is high in summer and low in winter. This has the disadvantage that the temperature of the hot water in winter drops.
本発明は上記欠点に鑑み、構成が簡単で、起動負荷変動
双方の制御が可能であり、かつ、冬期の出湯温度を上げ
る冷却液量制御方法を提供するものである。In view of the above-mentioned drawbacks, the present invention provides a cooling liquid amount control method that has a simple configuration, is capable of controlling both starting load fluctuations, and increases the hot water temperature in winter.
以下本発明の一実施例について、図面を参照しながら説
明する。第２図は本発明の一実施例における吸収式ヒー
トポンプ装置の冷却液量制御方法を示すものである。第
２図において、１１は吸収器、１２は溶液ポンプ、１３
は溶液熱交換器、１４は発生器、１５は凝縮器、１６は
膨張弁、１７は蒸発器、１８は放熱器（または貯湯槽）
、１９はポンプ、２０は定温度流量調節弁である。An embodiment of the present invention will be described below with reference to the drawings. FIG. 2 shows a method for controlling the amount of coolant in an absorption heat pump device according to an embodiment of the present invention. In FIG. 2, 11 is an absorber, 12 is a solution pump, and 13 is an absorber.
is a solution heat exchanger, 14 is a generator, 15 is a condenser, 16 is an expansion valve, 17 is an evaporator, 18 is a radiator (or hot water storage tank)
, 19 is a pump, and 20 is a constant temperature flow control valve.
次に、その動作を説明する。定温度流量調節弁２０は、
吸収器１１の冷却液出口部に設置され、前記冷却液出口
温度によシその開度を調節するものである。つまり、冷
却液出口温度が低い場合には開度を絞り冷却液量を減少
させ、出口温度が高い場合には開度を大きくし冷却水量
を増加させる。Next, its operation will be explained. The constant temperature flow rate control valve 20 is
It is installed at the coolant outlet of the absorber 11, and its opening degree is adjusted according to the coolant outlet temperature. That is, when the coolant outlet temperature is low, the opening degree is reduced to reduce the amount of coolant, and when the outlet temperature is high, the opening degree is increased to increase the amount of cooling water.
ただし、開度は最小でも最大値の６〜２ｏ％程度の水量
が得られるように調節しである。これにより起動時にも
若干の冷却水が流れ吸収器１１の起動時の温度を検知で
きる。However, the degree of opening should be adjusted so that the minimum amount of water is about 6 to 20% of the maximum value. As a result, some cooling water flows even at the time of startup, and the temperature of the absorber 11 at the time of startup can be detected.
実際に本発明を用いて実験を行った結果、冷却水入口温
度５°Ｃ〜４２°Ｃ２負荷変動６０％〜１ｏ○係の冷房
および暖房について吸収式ヒートポンプ装置を運転する
ことが可能であり、かつ冷却液出口温度は運転条件に関
係なく６５°Ｃ±２°Ｃを得た。As a result of actual experiments using the present invention, it was possible to operate an absorption heat pump device for cooling and heating with a cooling water inlet temperature of 5°C to 42°C, 2 load fluctuations of 60% to 1o○, Moreover, the coolant outlet temperature was 65°C±2°C regardless of the operating conditions.
以上のように本発明は、構成が簡単で、起動。As described above, the present invention is simple to configure and easy to start.
負荷変動双方に対して制御が可能であり、かつ十分給湯
および暖房に利用可能な温水を提供することができ、そ
の実用的効果は犬なるものがある。It is possible to control both load fluctuations and provide sufficient hot water that can be used for hot water supply and space heating, and its practical effects are impressive.
以上のように本発明は、冷却液入口温度、負荷変動およ
び冷暖給湯の差異による吸収器１１の排熱量の変動にか
かわらず一定温度の冷却液が貯湯槽に入ｌることになり
吸収器の廃熱を利用する上で好都合である。容あ゛吸収
式ヒートポンプサイクルへの影響１才実用上問題のない
ものである。As described above, the present invention allows the coolant at a constant temperature to enter the hot water storage tank regardless of fluctuations in the amount of exhaust heat from the absorber 11 due to the coolant inlet temperature, load fluctuations, and differences in hot and cold water supply. This is convenient for utilizing waste heat. Effect on absorption heat pump cycle: No problems in practical use.
第１図は従来の吸収式ヒートポンプ装置の構成図、第２
図は本発明の一実施例における吸収式ヒートポンプ装置
の構成図である。
１１・・吸収器、１２・・・・・溶液ポンプ、１３・・
・・溶液熱交換器、１４ ・・・発生器、１５ ・・・
凝縮器、１６・・・・膨張弁、１７−・−・・蒸発器、
１８・−放熱器まだは貯湯槽、１９・・・・・ポンプ、
１０・−流量調節弁、２ｏ−・・・定温度流量調節弁。Figure 1 is a configuration diagram of a conventional absorption heat pump device, Figure 2
The figure is a configuration diagram of an absorption heat pump device according to an embodiment of the present invention. 11...Absorber, 12...Solution pump, 13...
...Solution heat exchanger, 14 ...Generator, 15 ...
Condenser, 16... expansion valve, 17-... evaporator,
18.--heat radiator still hot water storage tank, 19...pump,
10.--Flow rate control valve, 2o--. Constant temperature flow rate control valve.
Claims (1)
器で吸収式ヒートポンプを形成し、前記吸収器の冷却液
循環路に冷却液流量調節弁を配し、前記冷却液の前記吸
収器出口温度を所定の値に保つように前記調節弁を制御
することを特徴とする吸収式ヒートポンプ装置。At least a generator, an absorber, a condenser, an expansion valve, and an evaporator form an absorption heat pump, a coolant flow rate regulating valve is disposed in a coolant circulation path of the absorber, and the coolant exit temperature of the absorber is An absorption heat pump device characterized in that the control valve is controlled so as to maintain the value at a predetermined value.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57113509A JPS594862A (en) | 1982-06-29 | 1982-06-29 | Absorption type heat pump device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP57113509A JPS594862A (en) | 1982-06-29 | 1982-06-29 | Absorption type heat pump device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS594862A true JPS594862A (en) | 1984-01-11 |
Family
ID=14614131
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP57113509A Pending JPS594862A (en) | 1982-06-29 | 1982-06-29 | Absorption type heat pump device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS594862A (en) |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5552290U (en) * | 1978-10-02 | 1980-04-07 |
-
1982
- 1982-06-29 JP JP57113509A patent/JPS594862A/en active Pending
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5552290U (en) * | 1978-10-02 | 1980-04-07 |
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