JPH04136663A - Screw freezer - Google Patents
Screw freezerInfo
- Publication number
- JPH04136663A JPH04136663A JP25824890A JP25824890A JPH04136663A JP H04136663 A JPH04136663 A JP H04136663A JP 25824890 A JP25824890 A JP 25824890A JP 25824890 A JP25824890 A JP 25824890A JP H04136663 A JPH04136663 A JP H04136663A
- Authority
- JP
- Japan
- Prior art keywords
- compressor
- passage
- tank
- capacity operation
- pressure
- 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
- 239000007788 liquid Substances 0.000 claims abstract description 34
- 238000007906 compression Methods 0.000 claims description 19
- 230000006835 compression Effects 0.000 claims description 15
- 238000005057 refrigeration Methods 0.000 claims description 15
- 239000003507 refrigerant Substances 0.000 abstract description 32
- 238000000034 method Methods 0.000 abstract description 2
- 239000006200 vaporizer Substances 0.000 abstract 4
- 238000010586 diagram Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 238000001704 evaporation Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000012216 screening Methods 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
Landscapes
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は、スクリュー冷凍装置、詳しくは、スライド弁
をもち、容量制御可能としたスクリュー圧縮機と、凝縮
器及び蒸発器とを備えたスクリュー冷凍装置に関する。Detailed Description of the Invention (Industrial Application Field) The present invention relates to a screw refrigeration system, specifically a screw refrigeration system having a slide valve and a screw compressor capable of controlling capacity, a condenser, and an evaporator. Regarding refrigeration equipment.
（従来の技術）
この種スクリュー冷凍装置において、冷媒をスクリュー
圧縮機の圧縮過程途中に注入して、吐出ガス温度を制御
するエコノマイザ−・サイクルを形成するようにしたも
のは、第５図に示したように、凝縮器（Ｂ）と蒸発器（
Ｃ）との間に中間膨張タンク（Ｄ）を設け、この膨張タ
ンク（Ｄ）を、高温膨張弁（Ｅ）を介して前記凝縮器（
Ｂ）に連通させると共に、前記膨張タンク（Ｄ）のガス
域を、中間吸入管（Ｆ）を介して圧縮機（Ａ）の中間吸
入ボー） （Ｇ）に接続したものが知られている。(Prior art) A screw refrigeration system of this type in which refrigerant is injected during the compression process of the screw compressor to form an economizer cycle to control the discharge gas temperature is shown in Fig. 5. As shown, the condenser (B) and evaporator (
An intermediate expansion tank (D) is provided between the expansion tank (D) and the condenser (C) through a high temperature expansion valve (E).
It is known that the gas region of the expansion tank (D) is connected to the intermediate suction port (G) of the compressor (A) via an intermediate suction pipe (F).
所が、前記圧縮機（Ａ）を、例えばスライド弁を用い該
スライド弁の移動により容量制御可能とした冷凍装置に
おいては、前記スライド弁を移動して小容量運転に制御
する場合、前記中間吸入ポート（Ｇ）と吸入側とが連通
ずるため、エコノマイザ−サイクルの中間圧が低下し、
吸入圧とは糧等しくなるため、前記膨張タンク（Ｄ）か
ら蒸発器（Ｃ）へ冷媒が流れなくなり、部分負荷時には
運転ができなくなる問題が生ずるのである。However, in a refrigeration system in which the capacity of the compressor (A) can be controlled by moving the slide valve, for example, when moving the slide valve to control the compressor (A) to a small capacity operation, the intermediate suction Since the port (G) and the suction side communicate, the intermediate pressure of the economizer cycle decreases,
Since the suction pressure is equal to the suction pressure, the refrigerant does not flow from the expansion tank (D) to the evaporator (C), resulting in a problem that operation becomes impossible at partial load.
このような問題点を解決するため、遠心力によって液圧
を発生させこの液圧により膨張タンクから蒸発器へ過冷
却液を流通させ得るようにしたものが、例えば、特開昭
５８−２１０４４６号に開示されているようにすでに提
案されている。この冷凍装置は、第６図に示したように
、スクリュー圧縮機（Ａ）の吐出側に接続する凝縮器（
Ｂ）の出口側に貯留タンク（Ｈ）を、更に該貯留タンク
（Ｈ）の出口側に膨張弁（Ｉ）を介して蒸発器（Ｃ）を
接続して、該蒸発器（Ｃ）を前記圧縮機（Ａ）の吸入側
に接続する一方、前記膨張弁（Ｉ）の出口側に三方弁（
Ｊ）を設けると共に、前記圧縮機（Ａ）の先端部に、該
圧縮機（Ａ）で回転されるロータ（Ｋ）を内装するハウ
ジング（Ｌ）を設けて、前記膨張弁（Ｉ）から前記ハウ
ジング（Ｌ）に送られる液−ガス混合冷媒を遠心力によ
り液とガスに分離し、分離したガス冷媒を導管（Ｍ）を
介して前記圧縮機（Ａ）の吸入圧と吐出圧の中間圧が存
在する部位に設けたポート（Ｎ）に送るようにしたエコ
ノマイザ−サイクルを形成し、また、液冷媒を加圧して
前記蒸発器（Ｃ）に送るようにしたものである。尚、（
Ｐ）は前記圧縮機（Ａ）に接続したモータである。In order to solve these problems, a system that generates liquid pressure by centrifugal force and allows supercooled liquid to flow from an expansion tank to an evaporator using this liquid pressure is disclosed in, for example, Japanese Patent Application Laid-Open No. 58-210446. It has already been proposed as disclosed in . As shown in Fig. 6, this refrigeration system consists of a condenser (
A storage tank (H) is connected to the outlet side of B), and an evaporator (C) is connected to the outlet side of the storage tank (H) via an expansion valve (I). While connected to the suction side of the compressor (A), a three-way valve (
J), and a housing (L) containing a rotor (K) rotated by the compressor (A) is provided at the tip of the compressor (A), and The liquid-gas mixed refrigerant sent to the housing (L) is separated into liquid and gas by centrifugal force, and the separated gas refrigerant is passed through the conduit (M) to the intermediate pressure between the suction pressure and the discharge pressure of the compressor (A). An economizer cycle is formed in which the liquid refrigerant is sent to a port (N) provided at a location where the refrigerant is present, and the liquid refrigerant is pressurized and sent to the evaporator (C). still,(
P) is a motor connected to the compressor (A).
（発明が解決しようとする課題）
ところで、このスクリュー冷凍装置においては、中間圧
が吸入圧とは寸等しくなる小容量運転時前記ロータ（Ｋ
）の回転による遠心力により、前記ハウジング（Ｌ）に
送られた液冷媒が加圧されて、蒸発圧力より高圧にでき
るから、この液圧により過冷却された液冷媒を前記蒸発
器（Ｃ）に流すことができるのであるが、前記三方弁（
Ｊ）や前記ロータ（Ｋ）及び該ロータ（Ｋ）を内装する
ハウジング（Ｌ）等を別に設ける必要が生じ、冷凍装置
全体の構造が複雑になるし、また、前記ロータ（Ｋ）で
液冷媒を攪拌するのであるから、抵抗が増大し、圧縮機
性能を低下させる問題もあった。(Problem to be Solved by the Invention) By the way, in this screw refrigeration system, the rotor (K
) The liquid refrigerant sent to the housing (L) is pressurized by the centrifugal force caused by the rotation of the housing (L), and the pressure can be higher than the evaporation pressure. However, the three-way valve (
J), the rotor (K), and the housing (L) that houses the rotor (K) must be provided separately, which complicates the structure of the entire refrigeration system. Since the compressor is stirred, there is a problem in that resistance increases and compressor performance deteriorates.
本発明は以上のような問題に鑑みてなしたもので、その
目的は、中間膨張タンクを用いてエコノマイザ−サイク
ルを構成しながら、簡単な構成で、大容量運転時におけ
るエコノマイザ−能力を低下させずに小容量運転時でも
中間膨張タンクから液冷媒を蒸発器に流せ、安定した運
転が行えるようにする点である。The present invention was made in view of the above-mentioned problems, and its purpose is to reduce the economizer performance during large-capacity operation with a simple structure while configuring an economizer cycle using an intermediate expansion tank. This is to enable stable operation by allowing liquid refrigerant to flow from the intermediate expansion tank to the evaporator even during small-capacity operation.
（課題を解決するための手段）
上記目的を達成するために、本発明は、スライド弁（１
７）をもち、容量制御可能としたスクリュー圧縮機（１
）と、凝縮器（２）及び蒸発器（３）とを備えたスクリ
ュー冷凍装置において、前記凝縮器（２）の出口側に、
高温膨張弁（６）を介装した液管（５）を介して中間膨
張タンク（４）を接続し、該タンク（４）を低温膨張弁
（８）を介して前記蒸発器（３）に接続すると共に、前
記タンク（４）のガス域に開口する中間吸入配管（１０
）を前記圧縮機（１）のケーシング（１１）に設ける中
間吸入通路（１８）に接続する一方、前記スライド弁（
１７）に、大容量運転時前記中間吸入通路（１８）を前
記ケーシング（１１）における圧縮室（１５）に連通さ
せる大径通路（１９）と、小容量運転時前記中間吸入通
路（１８）を前記圧縮室（１５）に連通させる小径通路
（２０）とを設けたのである。(Means for Solving the Problems) In order to achieve the above object, the present invention provides a slide valve (1
7) with a screw compressor (1
), a condenser (2), and an evaporator (3), on the outlet side of the condenser (2),
An intermediate expansion tank (4) is connected via a liquid pipe (5) equipped with a high temperature expansion valve (6), and the tank (4) is connected to the evaporator (3) via a low temperature expansion valve (8). An intermediate suction pipe (10) is connected and opens to the gas area of the tank (4).
) is connected to the intermediate suction passage (18) provided in the casing (11) of the compressor (1), while the slide valve (
17), a large diameter passage (19) that communicates the intermediate suction passage (18) with the compression chamber (15) in the casing (11) during large capacity operation, and a large diameter passage (19) that communicates the intermediate suction passage (18) with the compression chamber (15) in the casing (11) during high capacity operation. A small diameter passage (20) communicating with the compression chamber (15) is provided.
（作用）
小容量運転時において、前記スライド弁（１７）に設け
た前記小径通路（２０）を介して前記中間吸入配管（１
０）を圧縮機（１）の圧縮室（１５）に連通させること
により、前記小径通路（２０）がガス冷媒の流通抵抗と
なり、前記中間吸入通路（１８）に連通ずる前記タンク
（４）のガス域の圧力を前記圧縮機（１）の吸入圧より
高くできる。この結果、この差圧を利用して前記タンク
（４）における液域の液冷媒を前記蒸発器（３）に流す
ことができる。従って、前記圧縮機（１）の中間圧と吸
入圧との差圧がなくなる小容量運転時でも前記中間膨張
タンク（４）の液域から液冷媒を蒸発器（３）に流すこ
とができ、大容量運転時は勿論、小容量運転時でもエコ
ノマイザ−サイクルを利用しながら、前記蒸発器（３）
において液冷媒を蒸発させることができる。(Function) During small capacity operation, the intermediate suction pipe (1
0) to the compression chamber (15) of the compressor (1), the small diameter passage (20) becomes a flow resistance for the gas refrigerant, and the tank (4) communicating with the intermediate suction passage (18) The pressure in the gas region can be higher than the suction pressure of the compressor (1). As a result, the liquid refrigerant in the liquid region in the tank (4) can be made to flow into the evaporator (3) using this differential pressure. Therefore, even during small capacity operation where there is no differential pressure between the intermediate pressure and suction pressure of the compressor (1), liquid refrigerant can flow from the liquid region of the intermediate expansion tank (4) to the evaporator (3), The evaporator (3) is operated while using the economizer cycle not only during large-capacity operation but also during small-capacity operation.
The liquid refrigerant can be evaporated.
（実施例）
第４図は、スクリュー冷凍装置における配管系統を概略
的に示したもので、スクリュー圧縮機（１）の吐出側に
は凝縮器（２）を、また、吸入側には蒸発器（３）を接
続すると共に、前記凝縮器（２）と前記蒸発器（３）と
の間に中間膨張タンク（４）を介装し、前記凝縮器（２
）と前記中間膨張タンク（４）とを接続する液管（５）
には高温膨張弁（６）を介装すると共に、前記中間膨張
タンク（４）と前記蒸発器（３）とを接続する液管（７
）には低温膨張弁（８）を介装して、前記凝縮器（２）
で液化する冷媒を前記中間膨張タンク（４）を介して前
記蒸発器（３）に流入させ、該蒸発器（３）で蒸発した
ガス冷媒を前記圧縮機（１）に戻るように循環させてい
る。又、前記中間膨張タンク（４）のガス域を、前記圧
縮機（１）の圧縮過程途中間位に設ける中間吸入ポート
（９）に連通の中間吸入通路（１８）に、中間吸入配管
（１０）を介して接続し、前記中間膨張タンク（４）か
ら中間吸入ガス冷媒を前記中間吸入配管（１０）及び中
間吸入通路（１８）を介して前記中間吸入ポート（９）
に注入するエコノマイザ−サイクルを形成する。(Example) Figure 4 schematically shows the piping system in a screw refrigeration system, with a condenser (2) on the discharge side of the screw compressor (1), and an evaporator on the suction side. (3), and an intermediate expansion tank (4) is interposed between the condenser (2) and the evaporator (3).
) and the intermediate expansion tank (4).
is equipped with a high temperature expansion valve (6) and a liquid pipe (7) connecting the intermediate expansion tank (4) and the evaporator (3).
) is equipped with a low-temperature expansion valve (8), and the condenser (2)
The refrigerant that is liquefied in the evaporator (3) is caused to flow into the evaporator (3) through the intermediate expansion tank (4), and the gas refrigerant evaporated in the evaporator (3) is circulated back to the compressor (1). There is. Further, the gas region of the intermediate expansion tank (4) is connected to an intermediate suction passage (18) that communicates with an intermediate suction port (9) provided midway through the compression process of the compressor (1). ) and connect the intermediate suction gas refrigerant from the intermediate expansion tank (4) to the intermediate suction port (9) via the intermediate suction pipe (10) and intermediate suction passage (18).
Form an economizer cycle that injects into the fuel.
前記スクリュー圧縮機（１）は第１図に示したようにケ
ーシング（１１）内にねじ（１２）をもったスクリュー
（１３）を回転可能に支持すると共に、該スクリュー（
１３）の両側には前記ねじ（１２）と係合するゲートロ
ーラ（１４）（１４）を回転可能に設けて、前記スクリ
ュー（１３）と各ゲートローラ（１４）（１４）との保
合によりガス冷媒を圧縮する圧縮室（１５）を形成して
いる。又前記ねじ（１２）の山頂を気密状に取り囲む前
記ケーシング（１１）の内面には、二つの摺動溝（１６
）（ＩＦ５）を設けて、これら溝＜１（３’）（１８）
に摺動自在にスライド弁（１７）を配置し、該スライド
弁（１７）をロッドを介して制御装置（図示しない）に
連動し、この制御装置の動作により摺動させて前記圧縮
機（１）の容量制御運転が行えるようにしている。As shown in FIG. 1, the screw compressor (1) rotatably supports a screw (13) having a thread (12) in a casing (11), and
Gate rollers (14) (14) that engage with the screw (12) are rotatably provided on both sides of the screw (13), and the screw (13) and each gate roller (14) (14) are engaged with each other. A compression chamber (15) is formed in which the gas refrigerant is compressed. Furthermore, two sliding grooves (16) are provided on the inner surface of the casing (11) that airtightly surrounds the top of the screw (12).
) (IF5) and these grooves <1 (3') (18)
A slide valve (17) is slidably disposed in the compressor (1), and the slide valve (17) is linked to a control device (not shown) via a rod, and is slid by the operation of the control device to control the compressor (1). ) capacity control operation is possible.
また、前記ケーシング（１１）の内面には前記中間吸入
ポート（９）を開口させると共に、前記中間吸入配管（
１０）に連通ずる中間吸入通路（１８）を前記スライド
弁（１７）（１７）の摺動溝（１Ｂ）（１６）を横断す
るように設けて、前記中間吸入ポート（９）に連通させ
ると共に、前記スライド弁（１７）に、第３図に示した
ように大径通路（１９）と小径通路（２０）とを設け、
大容量運転時には第１図に示すように大径通路（１９）
を介して、また、例えば７０％容量以下の小容量運転時
には第２図に示すように小径通路（２０）を介してそれ
ぞれ前記中間吸入通路（１８）を前記中間吸入ポート（
９）に連通できるように構成するのである。Further, the intermediate suction port (9) is opened on the inner surface of the casing (11), and the intermediate suction pipe (
An intermediate suction passage (18) communicating with the intermediate suction port (9) is provided so as to cross the sliding grooves (1B) (16) of the slide valves (17) (17), and communicates with the intermediate suction port (9). , the slide valve (17) is provided with a large diameter passage (19) and a small diameter passage (20) as shown in FIG.
During large-capacity operation, as shown in Figure 1, a large-diameter passageway (19)
Also, during small capacity operation, for example, 70% capacity or less, the intermediate suction passage (18) is connected to the intermediate suction port (
9).
更に詳記すると、第３図に示すように、前記スライド弁
（１７）における円弧状の摺動面側には、スライド方向
に延びる底の浅い入口側及び出口側の第１凹状溝（２１
）と入口側及び出口側の第２凹状溝（２２）とを設けて
、第１凹状溝（２１）には前記中間吸入通路（１８）と
は糧同じ大きさの大径通路（１９）を、また、第２凹状
溝（２２）には前記中間吸入通路（１８）より小径で抵
抗を発生させる小径通路（２０）をそれぞれ開口させ、
容量制御のため前記スライド弁（１７）が何れの位置に
摺動しても、前記中間吸入通路（１８）から供給される
中間吸入ガスが、前記入口側凹状溝（２１，２２）から
、前記大径通路（１９）又は小径通路（２０）を経て、
前記出口側凹状溝（２１，２２）から前記中間吸入ポー
ト（９）を介して前記ケーシング（１１）内に形成され
る前記圧縮室（１５）に注入できるように構成するので
ある。More specifically, as shown in FIG. 3, the arcuate sliding surface side of the slide valve (17) has first concave grooves (21
) and second concave grooves (22) on the inlet and outlet sides, and the first concave groove (21) has a large diameter passage (19) of the same size as the intermediate suction passage (18). , and each of the second concave grooves (22) is opened with a small diameter passage (20) that is smaller in diameter than the intermediate suction passage (18) and generates resistance,
No matter which position the slide valve (17) slides to for capacity control, the intermediate suction gas supplied from the intermediate suction passageway (18) is transferred from the inlet side concave groove (21, 22) to the Through the large diameter passage (19) or the small diameter passage (20),
It is configured so that it can be injected from the outlet side concave grooves (21, 22) through the intermediate suction port (9) into the compression chamber (15) formed in the casing (11).
次に以上のように構成した実施例のスクリュー冷凍装置
の作用を説明する。Next, the operation of the screw refrigeration system according to the embodiment configured as above will be explained.
先ず、前記凝縮器（２）から前記液管（５）を流れる冷
媒は、前記高温膨張弁（６）により一部気化し、ガス−
液混合冷媒となってフラッシュしながら前記タンク（４
）に流入する。そし５て、大容量運転時には第１図に示
すように前記スライド弁（１７）に設けた前記大径通路
（１９）が前記中間吸入通路（１８）に連通し、該大径
通路（１９）を介して前記中間吸入通路（１８）が前記
中間吸入ボート（９）に連通ずるのであって、前記中間
膨張タンク（４）のガス域からガス冷媒は前記中間吸入
通路（１８）及び大径通路（１９）を介して前記中間吸
入ポート（９）から前記圧縮室（１５）における圧縮過
程途中に注入される一方、前記タンク（４）の液冷媒は
、該タンク（４）の下部に接続した前記液管（７）を流
れて前記低温膨張弁（８）で膨張し、そして前記蒸発器
（３）にて蒸発して前記圧縮機（１）に吸入される。First, the refrigerant flowing from the condenser (2) through the liquid pipe (5) is partially vaporized by the high temperature expansion valve (6) and becomes a gas.
It becomes a liquid mixed refrigerant and flashes into the tank (4).
). 5. During large capacity operation, as shown in FIG. 1, the large diameter passage (19) provided in the slide valve (17) communicates with the intermediate suction passage (18), and the large diameter passage (19) The intermediate suction passageway (18) communicates with the intermediate suction boat (9) through the intermediate suction passageway (18), and the gas refrigerant is transferred from the gas region of the intermediate expansion tank (4) to the intermediate suction passageway (18) and the large diameter passageway. (19) from the intermediate suction port (9) to the compression chamber (15) during the compression process, while the liquid refrigerant in the tank (4) is injected from the intermediate suction port (9) through the tank (4). It flows through the liquid pipe (7), expands in the low temperature expansion valve (8), evaporates in the evaporator (3), and is sucked into the compressor (1).
しかして、小容量運転時には第２図に示すように前記ス
ライド弁（１７）に設けた前記小径通路（２０）が前記
中間吸入通路（１８）に連通し、この小径通路（２０）
を介して前記中間吸入通路（１８）を前記中間吸入ポー
ト（９）に連通ずるのであって、前記中間膨張タンク（
４）のガス域からガス冷媒は前記中間吸入通路（１８）
及び小径通路（２０）を介して前記中間吸入ボート（９
）から前記圧縮室（１５）における圧縮過程途中に注入
され、エコノマイザ−サイクルを利用できるのである。Therefore, during small capacity operation, as shown in FIG. 2, the small diameter passage (20) provided in the slide valve (17) communicates with the intermediate suction passage (18), and the small diameter passage (20)
The intermediate suction passage (18) is communicated with the intermediate suction port (9) via the intermediate expansion tank (
The gas refrigerant from the gas region of 4) is transferred to the intermediate suction passage (18).
and the intermediate suction boat (9) via the small diameter passage (20).
) is injected into the compression chamber (15) during the compression process, making it possible to utilize the economizer cycle.
このとき、前記小径通路（２０）がガス冷媒の流通抵抗
となるから該小径通路（２０）に前記中間吸入配管（１
０）を介して連通ずる前記タンク（４）の圧力は前記圧
縮機（１）の吸入圧、換言すると、前記蒸発器（３）の
蒸発圧力より高くなり、前記タンク（４）の液域の液冷
媒は、この圧力差によって該タンク（４）の下部に接続
した前記液管（７）から前記蒸発器（３）に流れるので
ある。At this time, since the small diameter passage (20) becomes a flow resistance for the gas refrigerant, the intermediate suction pipe (1) is connected to the small diameter passage (20).
The pressure of the tank (4) communicated through the tank (4) is higher than the suction pressure of the compressor (1), in other words, the evaporation pressure of the evaporator (3), and the liquid area of the tank (4) is Due to this pressure difference, the liquid refrigerant flows from the liquid pipe (7) connected to the lower part of the tank (4) to the evaporator (3).
尚、以上の実施例では、前記スライド弁（１７）に底の
浅い凹状溝（２１）（２２）を設けたが、前記スライド
弁（１７）を摺動自在に支持する）前記各摺動溝（１６
）（１Ｂ）に形成してもよいのである。In the above embodiment, the slide valve (17) is provided with shallow concave grooves (21) and (22), but each of the slide grooves (which slidably support the slide valve (17)) (16
) (1B).
（発明の効果）
以上説明したように、本発明によれば、スライド弁（１
７）をもち、容量制御可能としたスクリュー圧縮機（１
）と、凝縮器（２）及び蒸発器（３）とを備えたスクリ
ュー冷凍装置において、前記凝縮器（２）の出口側に、
高温膨張弁（６）を介装した液管（５）を介して中間膨
張タンク（４）を接続し、該タンク（４）を低温膨張弁
（８）を介して前記蒸発器（３）に接続すると共に、前
記タンク（４）のガス域に開口する中間吸入配管（１０
）を前記圧縮機（１）のケーシング（１１）に設ける中
間吸入通路（１８）に接続する一方、前記スライド弁（
１７）に、大容量運転時前記中間吸入通路（１８）を前
記ケーシング（１１）における圧縮室（１５）に連通さ
せる大径通路（１９）と、小容量運転時前記中間吸入通
路（１８）を前記圧縮室（１５）に連通させる小径通路
（２０）とを設けたから、小容量運転時、前記スライド
弁（１７）に設けた前記小径通路（２０）を介して前記
中間吸入通路（１８）を圧縮機（１）の圧縮室（１５）
に連通させることにより、前記小径通路（２０）がガス
冷媒の流通抵抗となり、前記中間吸入通路（１８）に連
通ずる前記タンク（４）のガス域の圧力を前記圧縮機（
１）の吸入圧より高くできる。この結果、この差圧を利
用して前記タンク（４）における液域の液冷媒を、前記
蒸発器（３）に流し蒸発させることができる。従って、
安価な中間膨張タンクを用いながら、しかも、簡単な構
成の追加により前記圧縮機（１）の中間圧と吸入圧との
差圧がなくなる小容量運転時でも前記中間膨張タンク（
４）の液域から液冷媒を蒸発器（３）に流し、安定した
運転ができるのであり、また大容量運転時に抵抗が生ず
ることはないので能力が低下することもないのであって
、大容量運転時は勿論、小容量運転時でもエコノマイザ
−サイクルを利用した冷凍運転が可能となるのである。(Effect of the invention) As explained above, according to the present invention, the slide valve (1
7) with a screw compressor (1
), a condenser (2), and an evaporator (3), on the outlet side of the condenser (2),
An intermediate expansion tank (4) is connected via a liquid pipe (5) equipped with a high temperature expansion valve (6), and the tank (4) is connected to the evaporator (3) via a low temperature expansion valve (8). An intermediate suction pipe (10) is connected and opens to the gas area of the tank (4).
) is connected to the intermediate suction passage (18) provided in the casing (11) of the compressor (1), while the slide valve (
17), a large diameter passage (19) that communicates the intermediate suction passage (18) with the compression chamber (15) in the casing (11) during large capacity operation, and a large diameter passage (19) that communicates the intermediate suction passage (18) with the compression chamber (15) in the casing (11) during high capacity operation. Since a small diameter passage (20) communicating with the compression chamber (15) is provided, during small capacity operation, the intermediate suction passage (18) can be connected to the intermediate suction passage (18) through the small diameter passage (20) provided in the slide valve (17). Compression chamber (15) of compressor (1)
By communicating with the intermediate suction passage (18), the small diameter passage (20) becomes a flow resistance for the gas refrigerant, and the pressure in the gas region of the tank (4) communicating with the intermediate suction passage (18) is reduced by the compressor (
The suction pressure can be higher than 1). As a result, the liquid refrigerant in the liquid region in the tank (4) can be caused to flow into the evaporator (3) and evaporated using this differential pressure. Therefore,
By using an inexpensive intermediate expansion tank, and by adding a simple configuration, the intermediate expansion tank (
The liquid refrigerant flows into the evaporator (3) from the liquid area of 4), allowing stable operation.Also, there is no resistance during large capacity operation, so the capacity does not decrease. Refrigeration operation using the economizer cycle becomes possible not only during operation but also during small capacity operation.
第１図は、本発明のスクリュー冷凍装置の要部断面図、
第２図は同作動図、第３図はスライド弁の展開図、第４
図はスクリュー冷凍装置の概略第５図及び第６図は従来
例を示す説
配管系統図、
明図である。
（１）・・・・・・・・・・・・・・・スクリ（２）・
・・・・・・・・・・・・・・凝縮器（３）・・・・・
・・・・・・・・・・蒸発器（４）・・・・・・・・・
・・・・・・中間膨張タンク（５）・・・・・・・・・
・・・・・・液管（６）・・・・・・・・・・・・・・
・高温膨張弁（８）・・・・・・・・・・・・・・・低
温膨張弁（１０）・・・・・・・・・・・・中間吸入配
管（１１）・・・・・・・・・・・・ケーシング（１５
）・・・・・・・・・・・・圧縮室（１７）・・・・・
・・・・・・・スライド弁（１８）・・・・・・・・・
・・・中間吸入通路（１９）・・・・・・・・・・・・
大径通路（２０）・・・・・・・・・・・・小径通路ュ
ー圧縮機
第８図
第４図
１０：中藺唯人配管
１図
第５図
第６図
手続補正書
平成 ３年１１月２９日FIG. 1 is a sectional view of the main parts of the screw refrigeration device of the present invention,
Figure 2 is a diagram of the same operation, Figure 3 is an exploded view of the slide valve, and Figure 4 is an exploded view of the slide valve.
The figure is a schematic diagram of a screw refrigeration system. Figures 5 and 6 are an explanatory piping system diagram and a clear diagram showing a conventional example. (1)・・・・・・・・・・・・Screening (2)・
・・・・・・・・・・・・Condenser (3)・・・・・・
・・・・・・・・・Evaporator (4)・・・・・・・・・
・・・・・・Intermediate expansion tank (5)・・・・・・・・・
・・・・・・Liquid pipe (6)・・・・・・・・・・・・・・・
・High temperature expansion valve (8)...Low temperature expansion valve (10)...Intermediate suction pipe (11)...・・・・・・Casing (15
)......Compression chamber (17)...
......Slide valve (18)...
・・・Intermediate suction passage (19)・・・・・・・・・・・・
Large Diameter Passage (20)...Small Diameter Passage Compressor Figure 8 Figure 4 Figure 10: Chuai Yuito Piping 1 Figure 5 Figure 6 Procedure Amendment November 1991 29th
Claims (1)
クリュー圧縮機（１）と、凝縮器（２）及び蒸発器（３
）とを備えたスクリュー冷凍装置において、前記凝縮器
（２）の出口側に、高温膨張弁（８）を介装した液管（
５）を介して中間膨張タンク（４）を接続し、該タンク
（４）を低温膨張弁（８）を介して前記蒸発器（３）に
接続すると共に、前記タンク（４）のガス域に開口する
中、間吸入配管（１０）を前記圧縮機（１）のケーシン
グ（１１）に設ける中間吸入通路（１８）に接続する一
方、前記スライド弁（１７）に、大容量運転時前記中間
吸入通路（１８）を前記ケーシング（１１）における圧
縮室（１５）に連通させる大径通路（１９）と、小容量
運転時前記中間吸入通路（１８）を前記圧縮室（１５）
に連通させる小径通路（２０）とを設けたことを特徴と
するスクリュー冷凍装置。1) A screw compressor (1) with a slide valve (17) that allows for capacity control, a condenser (2), and an evaporator (3).
), a liquid pipe (
5) to an intermediate expansion tank (4), which is connected to the evaporator (3) via a cold expansion valve (8) and to the gas region of the tank (4). While opening, the intermediate suction pipe (10) is connected to the intermediate suction passage (18) provided in the casing (11) of the compressor (1), while the slide valve (17) is connected to the intermediate suction pipe (10) during large capacity operation. A large diameter passage (19) that communicates the passage (18) with the compression chamber (15) in the casing (11), and a large diameter passage (19) that connects the intermediate suction passage (18) with the compression chamber (15) during small capacity operation.
A screw refrigeration system characterized by being provided with a small diameter passageway (20) communicating with the screw refrigeration system.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25824890A JPH0820137B2 (en) | 1990-09-26 | 1990-09-26 | Screw refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25824890A JPH0820137B2 (en) | 1990-09-26 | 1990-09-26 | Screw refrigeration equipment |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH04136663A true JPH04136663A (en) | 1992-05-11 |
| JPH0820137B2 JPH0820137B2 (en) | 1996-03-04 |
Family
ID=17317590
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25824890A Expired - Fee Related JPH0820137B2 (en) | 1990-09-26 | 1990-09-26 | Screw refrigeration equipment |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0820137B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014192898A1 (en) | 2013-05-30 | 2014-12-04 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| WO2016046908A1 (en) * | 2014-09-24 | 2016-03-31 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| WO2016046907A1 (en) * | 2014-09-24 | 2016-03-31 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| WO2016084176A1 (en) * | 2014-11-26 | 2016-06-02 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
-
1990
- 1990-09-26 JP JP25824890A patent/JPH0820137B2/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014192898A1 (en) | 2013-05-30 | 2014-12-04 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| JP6058133B2 (en) * | 2013-05-30 | 2017-01-11 | 三菱電機株式会社 | Screw compressor and refrigeration cycle apparatus |
| WO2016046908A1 (en) * | 2014-09-24 | 2016-03-31 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| WO2016046907A1 (en) * | 2014-09-24 | 2016-03-31 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| JPWO2016046908A1 (en) * | 2014-09-24 | 2017-04-27 | 三菱電機株式会社 | Screw compressor and refrigeration cycle equipment |
| JPWO2016046907A1 (en) * | 2014-09-24 | 2017-04-27 | 三菱電機株式会社 | Screw compressor and refrigeration cycle equipment |
| WO2016084176A1 (en) * | 2014-11-26 | 2016-06-02 | 三菱電機株式会社 | Screw compressor and refrigeration cycle device |
| JPWO2016084176A1 (en) * | 2014-11-26 | 2017-04-27 | 三菱電機株式会社 | Screw compressor and refrigeration cycle equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0820137B2 (en) | 1996-03-04 |
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