JPH05113233A - Condensing pressure control system of condensation difference heat accumulation device - Google Patents
Condensing pressure control system of condensation difference heat accumulation deviceInfo
- Publication number
- JPH05113233A JPH05113233A JP3273727A JP27372791A JPH05113233A JP H05113233 A JPH05113233 A JP H05113233A JP 3273727 A JP3273727 A JP 3273727A JP 27372791 A JP27372791 A JP 27372791A JP H05113233 A JPH05113233 A JP H05113233A
- Authority
- JP
- Japan
- Prior art keywords
- heat
- solution
- heat exchanger
- condensing pressure
- condensation
- 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
- Air Conditioning Control Device (AREA)
Abstract
Description
【0001】[0001]
【産業上の利用分野】本発明は、濃度差蓄熱装置に係
り、特に、溶液の濃縮を圧縮された加熱媒体により実施
する濃度差蓄熱装置の凝縮圧力制御方式に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a concentration difference heat storage device, and more particularly to a condensation pressure control system for a concentration difference heat storage device in which a solution is concentrated by a compressed heating medium.
【0002】[0002]
【従来の技術】従来の濃度差蓄熱装置では、特開昭62−
218773号公報に記載されている様に、加熱媒体の濃縮圧
力制御に関しては考慮されていなかった。2. Description of the Related Art A conventional concentration difference heat storage device is disclosed in Japanese Patent Laid-Open No. 62-
As described in Japanese Patent No. 218773, no consideration was given to controlling the concentration pressure of the heating medium.
【0003】[0003]
【発明が解決しようとする課題】上記従来技術では、外
部冷却源での凝縮熱量が大きすぎる場合に、加熱媒体の
凝縮圧力,温度が低下して溶液の濃縮が不可能になる問
題があった。In the above-mentioned prior art, when the amount of heat of condensation in the external cooling source is too large, there is a problem that the condensation pressure and temperature of the heating medium are lowered and the solution cannot be concentrated. ..
【0004】また、外部冷却源での凝縮熱量が小さすぎ
る場合に、加熱媒体の凝縮圧力,温度が上昇して、圧縮
機の運転が不可能になる問題があった。Further, when the amount of heat of condensation in the external cooling source is too small, the condensation pressure and temperature of the heating medium rise, which causes a problem that the compressor cannot be operated.
【0005】本発明の目的は、外部冷却源での凝縮熱量
を制御して、凝縮圧力を制御する事により、上記の問題
点を解決して、良好なる運転状態を提供することにあ
る。An object of the present invention is to solve the above problems and provide a good operating condition by controlling the amount of heat of condensation in an external cooling source to control the condensation pressure.
【0006】[0006]
【課題を解決するための手段】上記の課題を解決するた
め、加熱媒体の凝縮圧力または温度を検出する検出部お
よび検出部で検出されたデータにより外部冷却源での凝
縮熱量を制御する制御装置を設け、これにより外部冷却
源での凝縮熱量を制御する様にしたものである。In order to solve the above-mentioned problems, a controller for detecting the condensation pressure or temperature of a heating medium and a controller for controlling the amount of condensation heat in an external cooling source based on the data detected by the detector. Is provided so that the amount of heat of condensation in the external cooling source is controlled.
【0007】[0007]
【作用】検出部は、加熱媒体の凝縮圧力または温度を検
出する。このデータを制御装置に送信し、設定値より高
い場合には外部冷却源での凝縮熱量が小さくなるように
制御する。また、設定値より低い場合には外部冷却源で
の凝縮熱量が大きくなるように制御する。The detector detects the condensing pressure or temperature of the heating medium. This data is transmitted to the control device, and when it is higher than the set value, the amount of heat of condensation in the external cooling source is controlled to be small. When the value is lower than the set value, the amount of heat of condensation in the external cooling source is controlled to be large.
【0008】これによって、加熱媒体の凝縮圧力または
温度は、一定になる様に制御される。Thereby, the condensing pressure or temperature of the heating medium is controlled to be constant.
【0009】[0009]
【実施例】以下、本発明の一実施例を図1により、説明
する。DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIG.
【0010】図1は、この発明の系統図である。圧縮式
冷凍サイクルは、ターボ形,スクリュー形,往復形の圧
縮機1、圧縮機1に結合されたロータを駆動する駆動機
2,圧縮機1のガス出入口1i,1oに連絡された四方
切換え弁3、四方切換え弁3に連絡された第一熱交換器
4および第二熱交換器5、これら第一と第二の熱交換器
4,5間に配置された外部冷却源としての空冷熱交換器
6,空冷熱交換器ファン駆動モータ37,第一熱交換器
4に取り付けられた圧力伝送器36、これら圧縮機1,
四方切換え弁3、第一及び第二熱交換器4,5、及び空
冷熱交換器6を互いに作動的に連絡する配管7,8,
9,10,11,12,13,14,15,16、配管
9,10,12,13,15,16の途中に介在された
弁17,18,19,20,21,22、第一熱交換器
4での凝縮圧力を制御するための制御部38とから構成
されている。FIG. 1 is a system diagram of the present invention. The compression type refrigeration cycle includes a turbo type, a screw type, a reciprocating type compressor 1, a driving device for driving a rotor connected to the compressor 1, a four-way switching valve connected to gas inlets / outlets 1i, 1o of the compressor 1. 3, a first heat exchanger 4 and a second heat exchanger 5 connected to the four-way switching valve 3, and air-cooled heat exchange as an external cooling source arranged between the first and second heat exchangers 4 and 5. Unit 6, air-cooling heat exchanger fan drive motor 37, pressure transmitter 36 attached to the first heat exchanger 4, these compressors 1,
Pipes 7, 8 for operatively connecting the four-way switching valve 3, the first and second heat exchangers 4, 5 and the air-cooling heat exchanger 6 to each other.
9,10,11,12,13,14,15,16, valves 17,18,19,20,21,22, first heat interposed in the middle of piping 9,10,12,13,15,16 And a control unit 38 for controlling the condensation pressure in the exchanger 4.
【0011】第一,第二熱交換器4,5は、密閉状の容
器23に納められている。この密閉容器23は、第一,
第二の部屋23A,23Bに断熱壁24によって区画さ
れ、内部には吸収液と冷媒液たとえば臭化リチウムと
水,エチレングリコールとフレオンの混合液(以下単に
混合液と言う)が注入されている。区画壁24の上方側
には、両室23Aと23Bとを連絡する開口25が形成
されている。開口25には必要に応じて冷媒蒸気中の液
滴を分離するためのエリミネータなどの気液分離素子を
配置する。The first and second heat exchangers 4 and 5 are housed in a sealed container 23. This closed container 23 is
The second chambers 23A and 23B are partitioned by a heat insulating wall 24, and an absorbing liquid and a refrigerant liquid such as a mixed liquid of lithium bromide and water and ethylene glycol and Freon (hereinafter simply referred to as a mixed liquid) are injected into the inside. .. On the upper side of the partition wall 24, an opening 25 that connects the two chambers 23A and 23B is formed. A gas-liquid separation element such as an eliminator for separating droplets in the refrigerant vapor is arranged in the opening 25 as needed.
【0012】第一の部屋23A,第二の部屋23Bに
は、その上方部に熱交換コイル26,27が設置され、
また、底部に吸込管を連絡したポンプ28,29、熱交
換コイル26,27の上部に設置した散布ヘッダ30,
31、ポンプ28,29の吐出側と散布ヘッダ30,3
1とを連絡する配管32,33とからなる第一,第二の
散布装置34,35が設置されている。Heat exchange coils 26 and 27 are installed above the first chamber 23A and the second chamber 23B, respectively.
Also, pumps 28 and 29 having suction pipes connected to the bottom thereof, spray headers 30 installed above the heat exchange coils 26 and 27,
31, the discharge side of the pumps 28, 29 and the spray headers 30, 3
First and second spraying devices 34 and 35, which are composed of pipes 32 and 33 that communicate with 1, are installed.
【0013】次に動作を説明する。Next, the operation will be described.
【0014】弁17,18,19,20を開(弁19を
小開として膨張弁として機能させる)、弁22,21を
閉、四方切替弁3を連通方向が矢印Aとなる(図1に図
示の状態)ようにする。また、第一の部屋23Aには混
合液が注入されている。The valves 17, 18, 19, 20 are opened (the valve 19 is made small open to function as an expansion valve), the valves 22, 21 are closed, and the four-way switching valve 3 is communicated with an arrow A (see FIG. 1). (State shown). Further, the mixed liquid is injected into the first chamber 23A.
【0015】圧縮機1による圧縮によって媒体蒸気(一
般にはフロン系)は高温高圧となり、配管8,四方切替
弁3,配管9,弁17を経て第一熱交換器4に流れ、こ
こを流れる間に混合液を加熱し、混合液から冷媒を蒸発
させ、混合液の吸収液濃度を高くする。混合液を加熱し
た結果、第一熱交換器4の媒体は液化し、配管10,弁
18,空冷熱交換器6,配管11,配管12,弁19を
経由し、弁19で減圧されて第二熱交換器5に流入す
る。この媒体液は、第二熱交換器5内で蒸発し、周囲
(第二の部屋23B)から蒸発潜熱を奪い、第一の部屋
23Aで蒸発し、開口25を通って流れ込んでくる第二
の部屋23B内の冷媒蒸気を液化させ部屋23Bの底部
に溜める。第二熱交換器5内で蒸発した媒体蒸気は、配
管13,弁20,配管14,四方切替弁3,配管7を経
由して圧縮機1に戻り、再び、圧縮機1で圧縮される。
この動作を継続する間に、第一の部屋23A内の混合液
は濃縮され、吸収液濃度がより高くなり、第二の部屋2
3Bには、第一の部屋23Aで蒸発させられた冷媒蒸気
を凝縮させた冷媒液が溜められる。これによって、第一
の部屋23A内の混合液は吸収能力が大きくなり、これ
に冷媒蒸気を吸収させれば吸収熱を発生する状態、言い
替えれば、蓄熱していることになる。また、第二の部屋
23Bの冷媒液は、液の状態にあるから蒸発する能力を
もっておりそのため、蒸発の際の蒸発潜熱に相当する冷
力を貯えている、すなわち、蓄冷していることになる。Due to the compression by the compressor 1, the medium vapor (generally a Freon system) becomes high temperature and high pressure, and flows through the pipe 8, the four-way switching valve 3, the pipe 9, and the valve 17 to the first heat exchanger 4, and while it flows there. The mixed liquid is heated to evaporate the refrigerant from the mixed liquid to increase the absorption liquid concentration of the mixed liquid. As a result of heating the mixed liquid, the medium of the first heat exchanger 4 is liquefied, passes through the pipe 10, the valve 18, the air-cooling heat exchanger 6, the pipe 11, the pipe 12, and the valve 19 and is decompressed by the valve 19 to It flows into the second heat exchanger 5. This medium liquid evaporates in the second heat exchanger 5, takes the latent heat of evaporation from the surroundings (the second chamber 23B), evaporates in the first chamber 23A, and flows in through the opening 25. The refrigerant vapor in the room 23B is liquefied and stored at the bottom of the room 23B. The medium vapor evaporated in the second heat exchanger 5 returns to the compressor 1 via the pipe 13, the valve 20, the pipe 14, the four-way switching valve 3 and the pipe 7, and is compressed by the compressor 1 again.
While continuing this operation, the mixed liquid in the first chamber 23A is concentrated, the concentration of the absorbing liquid becomes higher, and the second chamber 2
A refrigerant liquid obtained by condensing the refrigerant vapor evaporated in the first chamber 23A is stored in 3B. As a result, the mixed liquid in the first chamber 23A has a large absorption capacity, and if it absorbs the refrigerant vapor, it produces a heat of absorption, in other words, it stores heat. Further, the refrigerant liquid in the second chamber 23B has the ability to evaporate because it is in a liquid state, and therefore, it stores the cooling power corresponding to the latent heat of evaporation at the time of evaporation, that is, it stores cold. ..
【0016】ここで、第一熱交換器4に取り付けた圧力
伝送器36は、媒体の凝縮圧力信号を制御部38に送信
する。制御部38では設定圧力より凝縮圧力が低い場合
には空冷熱交換器ファン駆動モータ37の回転数を低下
させて、空冷熱交換器6での交換熱量が小さくし、第一
熱交換器4の凝縮圧力を上昇させる。また、制御部38
では設定圧力より凝縮圧力が高い場合には空冷熱交換器
ファン駆動モータ37の回転数を上昇させて、空冷熱交
換器6での交換熱量を大きくし、第一熱交換器4の凝縮
圧力を低下させる。Here, the pressure transmitter 36 attached to the first heat exchanger 4 sends a condensing pressure signal of the medium to the controller 38. When the condensing pressure is lower than the set pressure, the control unit 38 lowers the rotation speed of the air-cooling heat exchanger fan drive motor 37 to reduce the amount of heat exchanged in the air-cooling heat exchanger 6, thereby reducing the heat exchange amount of the first heat exchanger 4. Increase condensing pressure. In addition, the control unit 38
If the condensing pressure is higher than the set pressure, the rotation speed of the air-cooling heat exchanger fan drive motor 37 is increased to increase the amount of heat exchanged in the air-cooling heat exchanger 6 to increase the condensing pressure of the first heat exchanger 4. Lower.
【0017】このように第一熱交換器4の凝縮圧力を一
定に制御して、安定した蓄熱運転状態が提供される。In this way, the condensing pressure of the first heat exchanger 4 is controlled to be constant, and a stable heat storage operation state is provided.
【0018】[0018]
【発明の効果】本発明によれば、蓄熱運転中の第一熱交
換器の凝縮圧力を一定に制御できるので、安定した運転
状態を提供することができる。According to the present invention, since the condensing pressure of the first heat exchanger during the heat storage operation can be controlled to be constant, a stable operation state can be provided.
【図1】濃度差蓄熱装置の凝縮圧力制御方式の一実施例
の系統図。FIG. 1 is a system diagram of an example of a condensing pressure control system of a concentration difference heat storage device.
1…圧縮機、2…圧縮機用駆動モータ、3…四方切換
弁、4…第一熱交換器、36…圧力伝送器、37…空冷
熱交換器ファン駆動モータ、38…制御部。DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Compressor drive motor, 3 ... Four-way switching valve, 4 ... 1st heat exchanger, 36 ... Pressure transmitter, 37 ... Air-cooling heat exchanger fan drive motor, 38 ... Control part.
Claims (1)
した溶液が注入されている密閉容器状の第一および第二
の部屋と、前記第一および第二の部屋同士を連絡する蒸
気通路と、前記第一の部屋内に設置された第一熱交換器
および前記第二の部屋内に設置された第二熱交換器と、
前記第一および第二の熱交換器に連結された圧縮機と、
前記圧縮機の吐出側に連結された外部冷却源と、前記第
一および第二の部屋にそれぞれ別々に設置された溶液散
布装置とを備え、前記第一熱交換器および前記第二熱交
換器の一方の熱交換器および外部冷却源に加熱媒体圧縮
機で圧縮された加熱媒体蒸気を循環させ、残りの熱交換
器に冷却媒体として前記一方の熱交換器および外部冷却
源を出た媒体液を循環させて、前記一方の熱交換器で
は、溶液を加熱して冷媒蒸気を発生させて溶液を濃縮
し、この溶液の吸収能力を高くし、前記残りの熱交換器
では、前記一方の熱交換器で発生した冷媒蒸気を冷却液
化させて溶液の濃度を希薄にし、この溶液の蒸発能力を
高くし、熱エネルギを蓄積する濃度差蓄熱装置におい
て、前記外部冷却源での冷却熱量を増減させる事によ
り、前記加熱媒体蒸気の凝縮圧力を制御することを特徴
とする濃度差蓄熱装置の凝縮圧力制御方式。1. A first and a second chamber in the form of a closed container, into which a refrigerant, an absorbent or a solution in which these are mixed are injected, and a steam passage for connecting the first and the second chambers to each other. And a second heat exchanger installed in the first room and a first heat exchanger installed in the second room,
A compressor connected to the first and second heat exchangers,
An external cooling source connected to the discharge side of the compressor, and a solution spraying device separately installed in the first and second chambers, respectively, the first heat exchanger and the second heat exchanger. The heating medium vapor compressed by the heating medium compressor is circulated in one of the heat exchangers and the external cooling source, and the medium liquid that has flowed out of the one of the heat exchangers and the external cooling source as a cooling medium in the remaining heat exchangers. In one of the heat exchangers, the solution is heated to generate a refrigerant vapor to concentrate the solution, and the absorption capacity of the solution is increased. In the concentration difference heat storage device that cools and liquefies the refrigerant vapor generated in the exchanger to dilute the concentration of the solution, enhances the evaporation ability of this solution, and increases or decreases the amount of cooling heat in the external cooling source in the concentration difference heat storage device that stores heat energy. The heating medium vapor condenses Condensation pressure control method of the density difference the heat storage apparatus characterized by controlling the pressure.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3273727A JPH05113233A (en) | 1991-10-22 | 1991-10-22 | Condensing pressure control system of condensation difference heat accumulation device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3273727A JPH05113233A (en) | 1991-10-22 | 1991-10-22 | Condensing pressure control system of condensation difference heat accumulation device |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH05113233A true JPH05113233A (en) | 1993-05-07 |
Family
ID=17531724
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP3273727A Pending JPH05113233A (en) | 1991-10-22 | 1991-10-22 | Condensing pressure control system of condensation difference heat accumulation device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH05113233A (en) |
-
1991
- 1991-10-22 JP JP3273727A patent/JPH05113233A/en active Pending
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