JPH03236560A - Refrigerant direct expansion type air-conditioner - Google Patents
Refrigerant direct expansion type air-conditionerInfo
- Publication number
- JPH03236560A JPH03236560A JP2943090A JP2943090A JPH03236560A JP H03236560 A JPH03236560 A JP H03236560A JP 2943090 A JP2943090 A JP 2943090A JP 2943090 A JP2943090 A JP 2943090A JP H03236560 A JPH03236560 A JP H03236560A
- Authority
- JP
- Japan
- Prior art keywords
- heat exchanger
- refrigerant
- heat
- air
- 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.)
- Granted
Links
- 239000003507 refrigerant Substances 0.000 title claims abstract description 41
- 239000007788 liquid Substances 0.000 claims abstract description 16
- 238000001816 cooling Methods 0.000 abstract description 8
- 230000002159 abnormal effect Effects 0.000 abstract description 5
- 230000000694 effects Effects 0.000 abstract description 4
- 238000010438 heat treatment Methods 0.000 abstract description 2
- 238000000034 method Methods 0.000 abstract 1
- 239000000203 mixture Substances 0.000 abstract 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000005057 refrigeration Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
Landscapes
- Air Conditioning Control Device (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
【発明の詳細な説明】
「産業上の利用分野」
本発明は、冷媒直膨式空調装置に係わり、特に、冷媒ホ
ットガスを利用して冷房空気の湿度を調整する空調装置
に関する。DETAILED DESCRIPTION OF THE INVENTION "Field of Industrial Application" The present invention relates to a refrigerant direct expansion air conditioner, and particularly to an air conditioner that adjusts the humidity of cooled air using refrigerant hot gas.
Ｆ従来の技術Ｊ
従来より、ビルその他の室内冷房を行う空調装置におい
ては、冷凍若しくはヒートポンプサイクルを構成する熱
源機より冷熱エネルギーを付与された冷媒を、ユニット
クーラ内の熱交換器に直接給配し、その蒸発若しくは凝
縮熱を利用して空調を行う、いわゆる直膨式の空調装置
と、前記熱源機内の蒸発器若しくは凝縮器により熱供給
された冷温水（循環水）を介して前記ユニットクーラ内
の熱交換器に冷熱エネルギーの供給を行うようにした、
セントラル方式の空調装置等が存在するが、前者は冷媒
と室内空気が直接熱交換を行う為に熱効率の面で有利で
ある。F Conventional technology J Conventionally, in air conditioners that cool buildings and other rooms, refrigerant that has been given cold energy from a heat source device that constitutes a refrigeration or heat pump cycle is directly supplied and distributed to a heat exchanger in a unit cooler. The unit cooler is connected to a so-called direct expansion type air conditioner that performs air conditioning using the heat of evaporation or condensation, and cold/hot water (circulating water) supplied with heat by the evaporator or condenser in the heat source device. supply of cold energy to the heat exchanger inside the
Although there are central air conditioners, the former is advantageous in terms of thermal efficiency because the refrigerant and indoor air directly exchange heat.
「発明が解決しようとする課題」
しかしながら直膨型の空調装置においては冷媒と室内空
気が直接熱交換されるために、ユニットクーラよりの吹
出し温度が異常に低くなり、この為ユニットクーラ近傍
の者に不快感を与えることになる。``Problem to be solved by the invention'' However, in a direct expansion type air conditioner, the refrigerant and the indoor air directly exchange heat, so the temperature of the air blown out from the unit cooler becomes abnormally low. This will cause discomfort to the person.
この為、前記装置においては前記熱交換した冷却空気に
外気温度を混合させ、吹出し温度の異常温度低下を防い
でいるが、このように構成すると除湿されていない外気
がユニットクーラより噴出されることになる為に、特に
前記外気が高温多湿の場合に、室内状態を快適な湿度に
調整する事が不可能になる。For this reason, in the above device, outside air temperature is mixed with the heat-exchanged cooling air to prevent an abnormal drop in the blowout temperature, but with this configuration, outside air that has not been dehumidified may be blown out from the unit cooler. Therefore, especially when the outside air is hot and humid, it becomes impossible to adjust the indoor condition to a comfortable humidity level.
かかる欠点を解消する為に、前記冷凍サイクルを構成す
る圧縮機の吐出ガス（冷媒ホットガス）を利用して前記
異常冷却された吹出し空気を再加熱するように構成する
ことも可能であるが、このように構成すると前記吐出ガ
スが奪熱により凝縮された凝縮液の処理が困難になる。In order to eliminate this drawback, it is also possible to configure the abnormally cooled blown air to be reheated using the discharge gas (refrigerant hot gas) of the compressor constituting the refrigeration cycle. With this configuration, it becomes difficult to treat the condensate obtained by condensing the discharged gas due to heat removal.
即ち、ビル空調におけるセパレート型の空調装置におい
ては、室内に装着されるコントロールユニットその他の
室内空調機に対し、熱源機は一般に建物の屋上等に設置
する場合が多く、この為前記両機器の高低差により、空
調機排出後の凝縮液を屋上に設置された熱源機内の凝縮
器まで戻すのが困難で有り、又たとえ戻すことが可能だ
としても凝縮器内で液柱を押出す分の圧縮機吐出圧の増
加をも引起こすのみならず、動力増加を招く。In other words, in separate type air conditioners for building air conditioning, the heat source unit is generally installed on the roof of the building, etc., while the control unit and other indoor air conditioners are installed indoors. Due to the difference, it is difficult to return the condensed liquid discharged from the air conditioner to the condenser inside the heat source installed on the roof, and even if it is possible to return the condensed liquid, it is difficult to compress the liquid column by pushing out the liquid column in the condenser. This not only causes an increase in machine discharge pressure but also an increase in power.
この為前記両機器の高低差は、増加を許容出来る圧縮機
の最高吐出圧に制限を受け、無用に高い箇所に熱源機を
設置出来ないという欠点を有す。For this reason, the height difference between the two devices is limited by the maximum discharge pressure of the compressor that can be increased, and the heat source device cannot be installed at an unnecessarily high location.
一方前記吹出し空気の異常冷却はセントラル方式の場合
でも生じ、この為従来装置においては前記循環水の異常
冷却を防止するために、蒸発器若しくは熱交換器に導か
れる循環水をボイラその他の他エネルギー発生手段を利
用して予備加熱するように構成しているが、このように
構成すると、エネルギーの効率利用に反するのみならず
、設置コストが大になる。On the other hand, abnormal cooling of the blown air occurs even in the case of the central system.For this reason, in conventional equipment, in order to prevent abnormal cooling of the circulating water, the circulating water led to the evaporator or heat exchanger is used as a boiler or other energy source. Although the configuration is such that preheating is performed using a generating means, such a configuration not only goes against the efficient use of energy but also increases the installation cost.
本発明はかかる従来技術の欠点に鑑み、直膨式の空調装
置において、前記冷媒ホットガスを用いて吹出し空気の
温度制御を行うも、熱源機の設置位置に制限を受けたり
該熱源機側の動力増加を招く事なく、効率的に温度／湿
度制御が可能な空調装置を提供することを目的とする。In view of the drawbacks of the prior art, the present invention has been proposed in a direct expansion type air conditioner to control the temperature of the blown air using the refrigerant hot gas, but there are restrictions on the installation position of the heat source device and The purpose of the present invention is to provide an air conditioner that can efficiently control temperature/humidity without increasing power.
「課題を解決するための手段」
本発明はかかる技術的課題を達成する為に、室内空調機
としてのユニットクーラＩ内に２以上の熱交換器ＩＩ、
１２を設け、一の熱交換器１１に管路３１及び膨張弁
３２を介して前記熱源機２の凝縮器２１よりの液冷媒を
、又該熱交換器１１の下流側に位置する他の熱交換器１
２に圧縮機２２よりの吐出ガス冷媒を開閉可能な弁３３
（例えば流量調整や電磁開閉弁）を介して他の熱交換器
１２に夫々給配可能に構成すると共に、該第２の熱交換
器１２により熱交換されたガス冷媒を前記膨張弁３２と
一の熱交換器１１間の管路に導入可能に構成し、そして
より好ましくは前記第２の熱交換器１２により熱交換さ
れた冷媒の内、凝縮された液冷媒のみを膨張弁３２出口
直後の気液混層流中に導入可能に構成した事を特徴とす
る冷媒直膨式空調装置を提案する。"Means for Solving the Problem" In order to achieve the technical problem, the present invention provides two or more heat exchangers II in a unit cooler I as an indoor air conditioner,
12 is provided, and the liquid refrigerant from the condenser 21 of the heat source device 2 is supplied to one heat exchanger 11 through a pipe 31 and an expansion valve 32, and another heat exchanger located downstream of the heat exchanger 11 is supplied. exchanger 1
2, a valve 33 that can open and close the gas refrigerant discharged from the compressor 22;
The gas refrigerant heat exchanged by the second heat exchanger 12 is connected to the expansion valve 32. and more preferably, only the condensed liquid refrigerant of the refrigerant heat exchanged by the second heat exchanger 12 is introduced into the pipe line between the second heat exchangers 11. We propose a refrigerant direct expansion type air conditioner that is characterized by being configured so that it can be introduced into a gas-liquid mixed laminar flow.
「作用」
かかる技術手段によれば、室内空気の冷却を行なう一の
熱交換器１１の下流側に、圧縮機２２よりの吐出ガス冷
媒、言い換えればホットガス冷媒が導入される第２の熱
交換器１２を配した為に、前記一の熱交換器１１による
異常冷却を防止し、常に適正温度の吹出し空気を得るこ
とが出来るのみならず、温度制御用の特別の熱エネルギ
ー発生手段が不要となり、設備コストが大幅に低減する
。"Operation" According to this technical means, a second heat exchanger is introduced into which the gas refrigerant discharged from the compressor 22, in other words, the hot gas refrigerant, is introduced downstream of the first heat exchanger 11 that cools indoor air. By disposing the heat exchanger 12, abnormal cooling caused by the first heat exchanger 11 can be prevented, and not only can blown air at an appropriate temperature be obtained at all times, but also no special thermal energy generation means for temperature control is required. , equipment costs are significantly reduced.
又、吹出し空気は外気と混合されることなく、第２の熱
交換器１２の熱交換により温度制御がされるために、外
気の湿度状態と無関係に適切な温度／湿度制御が可能で
あり、而も前記第２の熱交換器１２に導入されるされる
ホット冷媒ガスは、開閉可能な弁３３を利用して開閉且
つ流量制御可能で有るために、前記効果が一層助長され
る。In addition, the temperature of the blown air is controlled by heat exchange in the second heat exchanger 12 without being mixed with the outside air, so appropriate temperature/humidity control is possible regardless of the humidity state of the outside air. Moreover, since the hot refrigerant gas introduced into the second heat exchanger 12 can be opened/closed and its flow rate controlled using the open/close valve 33, the above effect is further enhanced.
又、前記第２の熱交換器１２の熱交換により凝縮化され
たホット冷媒ガスは凝縮器２１側に戻すことなく、再度
一の熱交換器ＩＩ内に導入されて蒸発作用を営む為に熱
交換の有効利用が図れる。即ち第２の熱交換器１２と第
１の熱交換器ｌ１間で凝縮／蒸発サイクルを構成する為
に、熱損失が生ぜず、熱エネルギーの有効利用が図れる
。In addition, the hot refrigerant gas condensed by heat exchange in the second heat exchanger 12 is not returned to the condenser 21 side, but is introduced into the first heat exchanger II again to perform the evaporation action. Effective use of exchange can be achieved. That is, since a condensation/evaporation cycle is formed between the second heat exchanger 12 and the first heat exchanger l1, no heat loss occurs and thermal energy can be used effectively.
更に、前記第２の熱交換器１２により熱交換された前記
凝縮液は熱源機２側に戻入する必要がなく、ユニットク
ーラ１内で循環する構成を取る為に、前記冷媒ホットガ
スを用いて吹出し空気の温度制御を行うも、熱源機２の
設置位置に制限を受けたり該熱源機２側の動力増加を招
く事がない。Further, in order to adopt a configuration in which the condensed liquid heat-exchanged by the second heat exchanger 12 does not need to return to the heat source device 2 side and circulates within the unit cooler 1, the refrigerant hot gas is used. Even if the temperature of the blown air is controlled, the installation position of the heat source device 2 is not restricted and the power of the heat source device 2 is not increased.
「実施例」
以下、図面を参照して本発明の好適な実施例を例示的に
詳しく説明する。ただしこの実施例に記載されている構
成部品の寸法、材質、形状、その相対配置などは特に特
定的な記載がない限りは、この発明の範囲をそれのみに
限定する趣旨ではなく、単なる説明例に過ぎない。"Embodiments" Hereinafter, preferred embodiments of the present invention will be described in detail by way of example with reference to the drawings. However, unless otherwise specified, the dimensions, materials, shapes, and relative arrangements of the components described in this example are not intended to limit the scope of this invention, but are merely illustrative examples. It's nothing more than that.
第１図は本発明の実施例に係る空調装置のシステム構成
図である。FIG. 1 is a system configuration diagram of an air conditioner according to an embodiment of the present invention.
本装置はビルの屋上その他に設置された熱源機２と、各
室内に配置されたユニットクーラ１、及び該ユニットク
ーラ１の制御を行うユニットコントローラ３からなる。This device consists of a heat source device 2 installed on the roof of a building or elsewhere, a unit cooler 1 placed in each room, and a unit controller 3 that controls the unit cooler 1.
そして前記熱源機２は、モータ２２ａに連結されスライ
ド弁２２ｂにより圧力制御可能な冷凍圧縮機２２と、前
記圧縮機２２よりの吐出ガス冷媒の凝縮を行う凝縮器２
１とその凝縮液を貯溜するレシーバ詔、ユニットクーラ
１側で蒸発した冷媒ガスを貯溜するアキュームレータ２
４
を有し、圧縮機２２の吸気側へ接続され、前記吐出ガス
冷媒を凝縮器２１に導く管路は分岐されて電磁開閉弁３
３を介してユニットクーラ１内の第二の熱交換器１２内
に導入可能に構成されている。The heat source device 2 includes a refrigeration compressor 22 connected to a motor 22a and whose pressure can be controlled by a slide valve 22b, and a condenser 2 that condenses the gas refrigerant discharged from the compressor 22.
1, a receiver for storing the condensed liquid, and an accumulator 2 for storing the refrigerant gas evaporated on the unit cooler 1 side.
4, which is connected to the intake side of the compressor 22 and which leads the discharged gas refrigerant to the condenser 21, is branched and connected to the electromagnetic on-off valve 3.
3 so that it can be introduced into the second heat exchanger 12 in the unit cooler 1.
一方ユニットクーラ１は、上段側より順次エアーフィル
タ１３、第−及び第二の熱交換器１１．１２及び排気フ
ァン１４からなり、前記第１の熱交換器１１はその入口
側を管路３１及び膨張弁３２を介してレシーバ２３と、
又その出口側をアキュームレータ２４を介して圧縮機２
２の吸気側に接続する。On the other hand, the unit cooler 1 consists of an air filter 13, first and second heat exchangers 11, 12, and an exhaust fan 14 in this order from the upper stage side, and the first heat exchanger 11 has an inlet side connected to a pipe line 31 and an exhaust fan 14. receiver 23 via expansion valve 32;
Also, the outlet side is connected to the compressor 2 via the accumulator 24.
Connect to the intake side of 2.
一方策２の熱交換器１２は、前記電磁弁３３開放時に吐
出冷媒ガスが導入可能に構成され、又その出口側をフロ
ート式トレーナ１５及び管路３４を介して第１の熱交換
器１１の入口側に位置する膨張弁３２の出口直後に接続
させている。The heat exchanger 12 of the second option is configured such that the discharged refrigerant gas can be introduced when the electromagnetic valve 33 is opened, and the outlet side of the heat exchanger 12 is connected to the first heat exchanger 11 via the float trainer 15 and the pipe 34. It is connected immediately after the outlet of the expansion valve 32 located on the inlet side.
次にかかる実施例の作用を説明する。Next, the operation of this embodiment will be explained.
先ず熱源機２側では圧縮機２２により圧縮された吐出冷
媒ガスは凝縮器２１により凝縮された後レシーバ２３、
管路３７を介して各ユニットクーラ１の第１の熱交換器
１１内に導入され、モして該熱交換器１１で室内空気を
冷却する事により前記凝縮液が蒸発し、該蒸発冷媒ガス
を管路３８を介して熱源機２側に戻入し、アキュームレ
ータ２４を介して圧縮機２２の吸気°側に導入した後、
再度圧縮−凝縮一蒸発−戻入サイクルを繰り返す。First, on the heat source device 2 side, the discharged refrigerant gas compressed by the compressor 22 is condensed by the condenser 21, and then transferred to the receiver 23,
The condensed liquid is introduced into the first heat exchanger 11 of each unit cooler 1 through the pipe line 37, and the indoor air is cooled by the heat exchanger 11, whereby the condensed liquid evaporates, and the evaporated refrigerant gas is returned to the heat source device 2 side via the pipe line 38 and introduced into the intake side of the compressor 22 via the accumulator 24,
The compression-condensation-evaporation-return cycle is repeated again.
一方前記第１の熱交換器１１により冷却された吹出し空
気の温度が異常に低くなった場合は、該空気の温度若し
くは湿度を検知手段４０．４１により検知してユニット
コントローラ３よりの信号に基づいて電磁弁３３を開放
し、弁２５を閉じて吐出冷媒ガスを管路３９を介して第
２の熱交換器１２に導入し、第１の熱交換器１１により
冷却された室内空気を所定温度まで加温する。On the other hand, if the temperature of the blown air cooled by the first heat exchanger 11 becomes abnormally low, the temperature or humidity of the air is detected by the detection means 40.41 and based on the signal from the unit controller 3. The solenoid valve 33 is opened, the valve 25 is closed, and the discharged refrigerant gas is introduced into the second heat exchanger 12 via the pipe line 39, and the indoor air cooled by the first heat exchanger 11 is heated to a predetermined temperature. Warm up to.
そして前記加温により吐出冷媒ガスが凝縮されて第２の
熱交換器１２の出口側に排出され、そして該凝縮された
冷媒ガスはトレーナ１５及び管路３４を介してその凝縮
液のみを第１の熱交換器ｌｌ側の膨張弁３２出口側の気
液混相域に戻入され、再度第１の熱交換器１１内で所定
の冷却作用を営む。The discharged refrigerant gas is condensed by the heating and discharged to the outlet side of the second heat exchanger 12, and the condensed refrigerant gas is passed through the trainer 15 and the pipe 34 to the first It is returned to the gas-liquid multiphase region on the outlet side of the expansion valve 32 on the heat exchanger 11 side, and performs a predetermined cooling action within the first heat exchanger 11 again.
以下前記動作を繰り返す。Thereafter, the above operation is repeated.
「発明の効果」
以上記載した如く本発明によれば、ユニットクーラ１よ
りの吹出し空気は外気と混合されることなく、又特別の
熱エネルギー発生手段を設ける事なく、設備コストの低
減と吹出し空気を適正温度／湿度に維持し得る。"Effects of the Invention" As described above, according to the present invention, the air blown from the unit cooler 1 is not mixed with outside air, and there is no need to provide a special thermal energy generating means, thereby reducing equipment costs and reducing the blown air. can be maintained at appropriate temperature/humidity.
又、本発明は前記温度制御を行なうホット冷媒ガスは第
２の熱交換器１２で熱交換後、熱源機２側に戻す事なく
同一ユニットクーラ１内の第１の熱交換器１１に戻入さ
れる為に、熱損失が生ぜず、熱エネルギーの有効利用が
図れるとともに、熱源機２とユニットクーラｌに大きな
高低差があってもこれと無関係に且つ熱源機２側の動力
増加を招く事なく空調作用を営む事が出来る等の種々の
著効を有す。Further, in the present invention, the hot refrigerant gas that performs the temperature control is returned to the first heat exchanger 11 in the same unit cooler 1 after heat exchange in the second heat exchanger 12 without returning to the heat source device 2 side. Therefore, heat loss does not occur and thermal energy can be used effectively, and even if there is a large height difference between the heat source unit 2 and the unit cooler 1, it is possible to use the heat source unit 2 regardless of this difference and without causing an increase in power on the heat source unit 2 side. It has various effects such as being able to act as an air conditioner.
図面は本発明の実施例に係る空調装置のシステム構成図
である。The drawing is a system configuration diagram of an air conditioner according to an embodiment of the present invention.
Claims (1)
以上の熱交換器を含むユニットクーラとを有し、管路を
介して前記凝縮器よりの液冷媒を膨張弁を介して一の熱
交換器に、又圧縮機よりの吐出ガス冷媒を開閉可能な弁
を介して他の熱交換器に夫々給配可能に構成すると共に
、該第２の熱交換器により熱交換された冷媒を前記膨張
弁と一の熱交換器間の管路に導入可能に構成したことを
特徴とする冷媒直膨式空調装置 ２）前記第２の熱交換器により熱交換された冷媒の内、
凝縮された液冷媒のみを膨張弁出口直後に導入可能に構
成した事を特徴とする請求項１）記載の冷媒直膨式空調
装置[Claims] 1) A heat source device including a compressor and a condenser;
It has a unit cooler including the above heat exchanger, and can open and close the liquid refrigerant from the condenser through the condenser to one heat exchanger through the expansion valve, and the gas refrigerant discharged from the compressor. The refrigerant is configured to be able to be supplied and distributed to other heat exchangers through the respective expansion valves, and the refrigerant heat exchanged by the second heat exchanger can be introduced into the pipe line between the expansion valve and the first heat exchanger. 2) A refrigerant direct expansion type air conditioner characterized in that it is configured to: 2) Of the refrigerant heat exchanged by the second heat exchanger,
The refrigerant direct expansion type air conditioner according to claim 1), characterized in that the refrigerant direct expansion type air conditioner is configured such that only the condensed liquid refrigerant can be introduced immediately after the outlet of the expansion valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2943090A JP2813225B2 (en) | 1990-02-13 | 1990-02-13 | Refrigerant direct expansion air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2943090A JP2813225B2 (en) | 1990-02-13 | 1990-02-13 | Refrigerant direct expansion air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03236560A true JPH03236560A (en) | 1991-10-22 |
| JP2813225B2 JP2813225B2 (en) | 1998-10-22 |
Family
ID=12275927
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2943090A Expired - Fee Related JP2813225B2 (en) | 1990-02-13 | 1990-02-13 | Refrigerant direct expansion air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2813225B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008286444A (en) * | 2007-05-16 | 2008-11-27 | Toyo Eng Works Ltd | Air conditioning device |
-
1990
- 1990-02-13 JP JP2943090A patent/JP2813225B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008286444A (en) * | 2007-05-16 | 2008-11-27 | Toyo Eng Works Ltd | Air conditioning device |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2813225B2 (en) | 1998-10-22 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |