JP2017201216A - Turbo refrigerator - Google Patents

Turbo refrigerator Download PDF

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JP2017201216A
JP2017201216A JP2016092281A JP2016092281A JP2017201216A JP 2017201216 A JP2017201216 A JP 2017201216A JP 2016092281 A JP2016092281 A JP 2016092281A JP 2016092281 A JP2016092281 A JP 2016092281A JP 2017201216 A JP2017201216 A JP 2017201216A
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refrigerant
electric motor
liquid refrigerant
gas
turbo
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JP6630627B2 (en
Inventor
福住　幸大
Yukihiro Fukuzumi
幸大 福住
佐藤　忠
Tadashi Sato
忠 佐藤
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Ebara Refrigeration Equipment and Systems Co Ltd
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Ebara Refrigeration Equipment and Systems Co Ltd
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Abstract

PROBLEM TO BE SOLVED: To provide a turbo refrigerator capable of using both of a gas refrigerant and a liquid refrigerant or using only the gas refrigerant as a refrigerant that is supplied from a refrigeration cycle to an electric motor and is used for cooling the electric motor for driving a turbo compressor and of preventing deterioration of efficiency of a refrigerator by reducing agitation loss.SOLUTION: A turbo refrigerator includes: an evaporator 3 for evaporating a refrigerant by depriving cooling water of heat to exhibit a refrigeration effect; a turbo compressor 1 for compressing the refrigerant by using an impeller; an electric motor 12 for driving the turbo compressor 1; and a condenser 2 for cooling the compressed refrigerant by using cooling water for condensation. The turbo refrigerator further includes: gas refrigerant supply piping 6 for supplying a gas refrigerant from the condenser 2 to the electric motor 12; and liquid refrigerant supply piping 7 for supplying a liquid refrigerant from the condenser 2 to the electric motor 12. By using both of the gas refrigerant and the liquid refrigerant, the electric motor 12 is cooled.SELECTED DRAWING: Figure 2

Description

本発明は、ターボ冷凍機に係り、特にターボ圧縮機を駆動する電動機に冷凍サイクルか
ら冷媒の一部を導いて電動機を冷却する方式のターボ冷凍機に関するものである。 The present invention relates to a turbo chiller, and more particularly to a turbo chiller that cools an electric motor by introducing a part of refrigerant from a refrigeration cycle to an electric motor that drives the turbo compressor.

従来、冷凍空調装置などに利用されるターボ冷凍機は、冷媒を封入したクローズドシス
テムで構成され、冷水（被冷却流体）から熱を奪って冷媒が蒸発して冷凍効果を発揮する
蒸発器と、前記蒸発器で蒸発した冷媒ガスを圧縮して高圧の冷媒ガスにする圧縮機と、高
圧の冷媒ガスを冷却水（冷却流体）で冷却して凝縮させる凝縮器と、前記凝縮した冷媒を
減圧して膨張させる膨張弁（膨張機構）とを、冷媒配管によって連結して構成されている。 Conventionally, a turbo refrigerator used in a refrigeration air conditioner or the like is configured by a closed system in which a refrigerant is enclosed, an evaporator that takes heat from cold water (fluid to be cooled) and evaporates the refrigerant to exert a refrigeration effect; A compressor that compresses the refrigerant gas evaporated in the evaporator to form a high-pressure refrigerant gas; a condenser that cools and condenses the high-pressure refrigerant gas with cooling water (cooling fluid); and depressurizes the condensed refrigerant. An expansion valve (expansion mechanism) that is expanded by being connected by a refrigerant pipe.

ターボ冷凍機に用いられているターボ圧縮機は、電動機が圧縮機とともに分割型のケー
シングに密閉状態で収容されている半密閉型圧縮機を採用する場合が多い。この半密閉型
圧縮機においては、電動機の損失により生じた発熱を、冷凍サイクル中の凝縮冷媒（液冷
媒）を電動機内部に導入して冷媒の蒸発潜熱を利用して冷却する場合が多い。このように、電動機を液冷媒を用いて冷却する場合、電動機の回転体（ロータ）と過剰に散布された液冷媒とが接触して撹拌損失が大きくなり、その結果、電動機の損失が大きくなるため、冷凍機の効率が低下するという問題点がある。
一方、冷凍サイクル中のガス冷媒を用いて電動機を冷却する場合、ガス冷媒によって電動機から持ち去る熱量が小さいため、高負荷時の所要ガス量が多くなり、その結果、配管径およびモータ内部流路等の冷却用流路が大きくなり、装置が大型化するという問題点がある。 In many cases, a turbo compressor used in a turbo refrigerator employs a semi-hermetic compressor in which an electric motor is housed in a split casing together with a compressor. In this semi-hermetic compressor, the heat generated due to the loss of the electric motor is often cooled by introducing condensed refrigerant (liquid refrigerant) in the refrigeration cycle into the electric motor and using the latent heat of vaporization of the refrigerant. Thus, when the electric motor is cooled using liquid refrigerant, the rotating body (rotor) of the electric motor and the excessively dispersed liquid refrigerant come into contact with each other, resulting in an increase in stirring loss, resulting in an increase in electric motor loss. Therefore, there is a problem that the efficiency of the refrigerator is lowered.
On the other hand, when the electric motor is cooled using the gas refrigerant in the refrigeration cycle, the amount of heat required to be taken away from the electric motor by the gas refrigerant is small, so the required amount of gas at high load increases, resulting in the pipe diameter, motor internal flow path, etc. There is a problem that the cooling flow path becomes larger and the apparatus becomes larger.

特開２０１４−１５９９２３号公報JP 2014-159923 A 特開２０１４−１６３６２４号公報JP 2014-163624 A

本発明は、上述の事情に鑑みなされたもので、ターボ圧縮機を駆動する電動機の冷却用冷媒として冷凍サイクルから電動機に供給される冷媒を、ガス冷媒と液冷媒とを併用可能またはガス冷媒のみとすることができ、撹拌損失を低減させて冷凍機の効率低下を防止することができるターボ冷凍機を提供することを目的とする。   The present invention has been made in view of the above-described circumstances, and the refrigerant supplied to the electric motor from the refrigeration cycle as the refrigerant for cooling the electric motor that drives the turbo compressor can be used in combination with the gas refrigerant and the liquid refrigerant or only the gas refrigerant. An object of the present invention is to provide a turbo refrigerator that can reduce stirring loss and prevent a decrease in efficiency of the refrigerator.

上述の目的を達成するため、本発明のターボ冷凍機は、冷水から熱を奪って冷媒が蒸発し冷凍効果を発揮する蒸発器と、冷媒を羽根車によって圧縮するターボ圧縮機と、ターボ圧縮機を駆動する電動機と、圧縮された冷媒を冷却水で冷却して凝縮させる凝縮器とを備えたターボ冷凍機において、前記凝縮器から前記電動機にガス冷媒を供給するガス冷媒供給配管と、前記凝縮器から前記電動機に液冷媒を供給する液冷媒供給配管とを備え、前記電動機をガス冷媒と液冷媒とを併用して冷却するようにしたことを特徴とする。   In order to achieve the above object, a turbo refrigerator of the present invention includes an evaporator that takes heat from cold water and evaporates the refrigerant to exert a refrigeration effect, a turbo compressor that compresses the refrigerant with an impeller, and a turbo compressor A turbo chiller comprising a motor for driving the compressor and a condenser for cooling and condensing the compressed refrigerant with cooling water, a gas refrigerant supply pipe for supplying gas refrigerant from the condenser to the electric motor, and the condensation And a liquid refrigerant supply pipe for supplying liquid refrigerant to the electric motor from a container, wherein the electric motor is cooled by using a gas refrigerant and a liquid refrigerant together.

本発明の好ましい態様によれば、前記液冷媒供給配管に設置される液冷媒制御弁と、冷凍負荷を検出する手段を備え、ターボ冷凍機の負荷が所定の値よりも小さいときには、前記液冷媒制御弁を閉じ、前記電動機をガス冷媒のみで冷却するようにしたことを特徴とする。
本発明の好ましい態様によれば、前記ガス冷媒供給配管に設置されるガス冷媒制御弁と、冷凍負荷を検出する手段を備え、前記ガス冷媒制御弁を負荷に応じて開度制御することを特徴とする。
本発明の好ましい態様によれば、ターボ冷凍機の負荷が所定の値よりも大きいときには、ガス冷媒流量が１００％になるように前記ガス冷媒制御弁を制御し、さらに、前記液冷媒制御弁を前記負荷に応じて制御することを特徴とする。 According to a preferred aspect of the present invention, the liquid refrigerant control valve installed in the liquid refrigerant supply pipe and means for detecting a refrigeration load are provided, and when the load of the turbo chiller is smaller than a predetermined value, the liquid refrigerant The control valve is closed, and the electric motor is cooled only by a gas refrigerant.
According to a preferred aspect of the present invention, a gas refrigerant control valve installed in the gas refrigerant supply pipe and means for detecting a refrigeration load are provided, and the opening degree of the gas refrigerant control valve is controlled according to the load. And
According to a preferred aspect of the present invention, when the load of the centrifugal chiller is larger than a predetermined value, the gas refrigerant control valve is controlled so that the gas refrigerant flow rate becomes 100%, and the liquid refrigerant control valve is further controlled. Control is performed according to the load.

本発明の好ましい態様によれば、負荷が小さい場合に、前記制御弁をホットガスバイパス制御に使用することを特徴とする。
本発明の好ましい態様によれば、前記電動機から排出されるガス冷媒を駆動用ガスとして、前記電動機に溜まっている液冷媒を吸引して該液冷媒を電動機から排出するためのエジェクタを設け、前記エジェクタにより吸引された液冷媒は、前記蒸発器に戻されることを特徴とする。 According to a preferred aspect of the present invention, the control valve is used for hot gas bypass control when the load is small.
According to a preferred aspect of the present invention, there is provided an ejector that uses the gas refrigerant discharged from the electric motor as a driving gas, sucks the liquid refrigerant accumulated in the electric motor, and discharges the liquid refrigerant from the electric motor, The liquid refrigerant sucked by the ejector is returned to the evaporator.

本発明は、以下に列挙する効果を奏する。
１）ターボ圧縮機を駆動する電動機の冷却用冷媒として冷凍サイクルから電動機に供給
される冷媒を、ガス冷媒と液冷媒とを併用可能またはガス冷媒のみとすることができる。したがって、ターボ冷凍機の低負荷時はガス冷媒のみで電動機を冷却することができるため、撹拌損失が小さくて済み、また、凝縮器からエコノマイザを経由せずに蒸発器に流れる液冷媒を減らすことで冷凍機の効率低下を防止することができる。また、高負荷時はガス冷媒と液冷媒とを併用して電動機を冷却することができ、液冷媒をコイルなどの高温部に集中的に散布できるため、冷却能力が不足することはない。
２）ターボ冷凍機の低負荷時はガス冷媒のみで電動機を冷却することができるため、冷媒
ポンプの動力を削減することができる。
３）ターボ冷凍機は低負荷で運転されることが多いので、低負荷時の効率改善は効果的で
ある。
４）ガス冷媒のみでなく、液冷媒を併用することができるため、配管径およびモータ内部流路等の冷却用流路の簡素化を図ることができ、装置を小型化できる。 The present invention has the following effects.
1) As a refrigerant for cooling the electric motor that drives the turbo compressor, the refrigerant supplied from the refrigeration cycle to the electric motor can be used in combination with a gas refrigerant and a liquid refrigerant, or only the gas refrigerant can be used. Therefore, since the electric motor can be cooled only by the gas refrigerant when the turbo chiller is under a low load, the stirring loss is small, and the liquid refrigerant flowing from the condenser to the evaporator without going through the economizer is reduced. Thus, it is possible to prevent the efficiency of the refrigerator from decreasing. Further, when the load is high, the electric motor can be cooled by using both the gas refrigerant and the liquid refrigerant, and the liquid refrigerant can be intensively sprayed on a high temperature part such as a coil, so that the cooling capacity is not insufficient.
2) Since the electric motor can be cooled only by the gas refrigerant when the turbo refrigerator is under a low load, the power of the refrigerant pump can be reduced.
3) Since the centrifugal chiller is often operated at a low load, the efficiency improvement at the low load is effective.
4) Since not only a gas refrigerant but also a liquid refrigerant can be used together, simplification of a cooling flow path such as a pipe diameter and a motor internal flow path can be achieved, and the apparatus can be downsized.

図１は、本発明に係るターボ冷凍機の実施形態を示す模式図である。FIG. 1 is a schematic view showing an embodiment of a turbo refrigerator according to the present invention. 図２は、図１に示すターボ冷凍機におけるターボ圧縮機の電動機に冷却用冷媒を供給する構成を示す模式図である。FIG. 2 is a schematic diagram showing a configuration for supplying a cooling refrigerant to the electric motor of the turbo compressor in the turbo refrigerator shown in FIG. 図３は、図１に示すターボ冷凍機の負荷を判定する構成を示す模式図である。FIG. 3 is a schematic diagram showing a configuration for determining the load of the turbo refrigerator shown in FIG. 図４は、電動機を冷却した後の冷媒を蒸発器に戻すための構成を示す模式図である。FIG. 4 is a schematic diagram showing a configuration for returning the refrigerant after cooling the electric motor to the evaporator.

以下、本発明に係るターボ冷凍機の実施形態を図１乃至図４を参照して説明する。図１乃至図４において、同一または相当する構成要素には、同一の符号を付して重複した説明を省略する。
図１は、本発明に係るターボ冷凍機を示す模式図である。図１に示すように、ターボ冷凍機は、冷媒を圧縮するターボ圧縮機１と、圧縮された冷媒ガスを冷却水（冷却流体）で冷却して凝縮させる凝縮器２と、冷水（被冷却流体）から熱を奪って冷媒が蒸発し冷凍効果を発揮する蒸発器３と、凝縮器２と蒸発器３との間に配置される中間冷却器であるエコノマイザ４とを備え、これら各機器を冷媒が循環する冷媒配管５によって連結して構成されている。 Hereinafter, an embodiment of a turbo refrigerator according to the present invention will be described with reference to FIGS. 1 to 4. 1 to 4, the same or corresponding components are denoted by the same reference numerals, and redundant description is omitted.
FIG. 1 is a schematic view showing a turbo refrigerator according to the present invention. As shown in FIG. 1, a turbo refrigerator includes a turbo compressor 1 that compresses refrigerant, a condenser 2 that cools and compresses the compressed refrigerant gas with cooling water (cooling fluid), and cold water (cooled fluid). ), An evaporator 3 that evaporates the refrigerant and exerts a refrigeration effect, and an economizer 4 that is an intermediate cooler disposed between the condenser 2 and the evaporator 3. Are connected by a refrigerant pipe 5 that circulates.

図１に示す実施形態においては、ターボ圧縮機１は、多段ターボ圧縮機から構成されている。ターボ圧縮機１は、冷媒配管５によってエコノマイザ４と接続されており、エコノマイザ４で分離された冷媒ガスは多段ターボ圧縮機の多段の圧縮段（この例では２段）の中間部分（この例では一段目と二段目の間の部分）に導入されるようになっている。   In the embodiment shown in FIG. 1, the turbo compressor 1 is composed of a multistage turbo compressor. The turbo compressor 1 is connected to an economizer 4 by a refrigerant pipe 5, and the refrigerant gas separated by the economizer 4 is an intermediate portion (in this example, two stages) of a multistage turbo compressor (in this example, two stages). It is introduced in the part between the first stage and the second stage).

図１に示すように構成されたターボ冷凍機の冷凍サイクルでは、ターボ圧縮機１と凝縮器２と蒸発器３とエコノマイザ４とを冷媒が循環し、蒸発器３で冷水が製造されて負荷に対応し、冷凍サイクル内に取り込まれた蒸発器３からの熱量および圧縮機モータから供給されるターボ圧縮機１の仕事に相当する熱量が凝縮器２に供給される冷却水に放出される。一方、エコノマイザ４にて分離されたガス冷媒はターボ圧縮機１の多段圧縮段の中間部分に導入され、一段目圧縮機からのガス冷媒と合流して二段目圧縮機により圧縮される。２段圧縮単段エコノマイザサイクルによれば、エコノマイザ４による冷凍効果部分が付加されるので、その分だけ冷凍効果が増加し、エコノマイザ４を設置しない場合に比べて冷凍効果の高効率化を図ることができる。   In the refrigeration cycle of the turbo chiller configured as shown in FIG. 1, the refrigerant circulates through the turbo compressor 1, the condenser 2, the evaporator 3, and the economizer 4, and cold water is produced by the evaporator 3 to the load. Correspondingly, the amount of heat from the evaporator 3 taken into the refrigeration cycle and the amount of heat corresponding to the work of the turbo compressor 1 supplied from the compressor motor are released to the cooling water supplied to the condenser 2. On the other hand, the gas refrigerant separated by the economizer 4 is introduced into an intermediate portion of the multistage compression stage of the turbo compressor 1, merges with the gas refrigerant from the first stage compressor, and is compressed by the second stage compressor. According to the two-stage compression single-stage economizer cycle, since the refrigeration effect portion by the economizer 4 is added, the refrigeration effect is increased by that amount, and the efficiency of the refrigeration effect is increased as compared with the case where the economizer 4 is not installed Can do.

図２は、図１に示すターボ冷凍機におけるターボ圧縮機１の電動機１２に冷却用冷媒を供給する構成を示す模式図である。図２に示すように、ターボ冷凍機は、凝縮器２から電動機１２にガス冷媒を供給するガス冷媒供給配管６と、凝縮器２から電動機１２に液冷媒を供給する液冷媒供給配管７と、電動機１２を冷却した後の冷媒を蒸発器３に戻す冷却冷媒戻り配管８とを備えている。ガス冷媒供給配管６には、ガス冷媒制御弁ＶＧが設置され、液冷媒供給配管７には、冷媒ポンプ９と液冷媒制御弁ＶＬとが設置されている。 FIG. 2 is a schematic diagram showing a configuration for supplying a cooling refrigerant to the electric motor 12 of the turbo compressor 1 in the turbo refrigerator shown in FIG. As shown in FIG. 2, the turbo refrigerator includes a gas refrigerant supply pipe 6 that supplies a gas refrigerant from the condenser 2 to the electric motor 12, a liquid refrigerant supply pipe 7 that supplies a liquid refrigerant from the condenser 2 to the electric motor 12, A cooling refrigerant return pipe 8 for returning the refrigerant after cooling the electric motor 12 to the evaporator 3 is provided. The gas refrigerant supply pipe 6 is installed a gas refrigerant control valve V G, the liquid refrigerant supply pipe 7, the refrigerant pump 9 and the liquid refrigerant control valve V L is established.

次に、図２に示す構成を備えたターボ冷凍機においてターボ圧縮機１の電動機１２の冷却方法について説明する。
１）液冷媒とガス冷媒の併用による冷却
ｉ）本発明はエコノマイザを持つターボ冷凍機を対象とするが、エコノマイザが無くてもよい。ターボ冷凍機の電動機は液冷媒によって冷却することが一般的である。液冷媒は電動機の熱で蒸発し、おもにその潜熱で電動機を冷却する。
液冷媒は凝縮器２から冷媒ポンプ９によって電動機１２に供給する。圧力関係は、蒸発器≦電動機≦凝縮器 となるため、冷媒ポンプは無くても良い。蒸発したガスは圧力の低い蒸発器３に向けて排出する。凝縮器２やエコノマイザ４（図１参照）に排出することもできる。
ii）液冷媒を電動機内部に均一に行き渡らせ、すべて蒸発させることは技術的に困難である。実際には必要量の数倍の液冷媒を電動機１２の中に散布している。未蒸発の液冷媒は電動機１２の下部から蒸発器３に向けて排出される。この液冷媒はエコノマイザを経由しないので損失となり、冷凍機の効率を低下させる。
iii）一方、ガス冷媒で電動機１２を冷却する場合は液冷媒の排出はない。ガス冷媒は比熱が小さいため、電動機の発熱量をすべて冷却するには多大な流量を必要とする。大量のガスを供給するための大口径のガス流路が必要になる。電動機内の温度分布は均一ではなく、コイルなど電流が流れる部分が発熱して高温になる。
iv）そこで本発明では、電動機の高温部に向けて液冷媒を散布して効果的に冷却を行う。また、ガス冷媒の流入路も設けることで全体をガス冷媒で冷却する。これにより、電動機１２の冷却効果を落とすことなく、液冷媒の散布量を減らすことができる。液冷媒の排出量が減少し、冷凍機の効率が向上する。
２）電動機の負荷が小さいときには、ガス冷媒のみによる冷却
ｉ）冷凍機の負荷と電動機の発熱量とは相関する。冷凍機の負荷が高い時は発熱量が多い。負荷が低い時は発熱量が小さい。年間を通してみると、冷凍機は低い負荷で運転される時間が圧倒的に長い。低負荷時は電動機の発熱量が少ないので液冷媒の散布量を減らしても冷却ができる。さらに条件によっては、液冷媒の散布を止めてガス冷媒だけでも冷却ができる。
ii）そこで本発明では、液冷媒供給配管７に液冷媒制御弁ＶＬを設け、負荷に応じて液冷媒の散布量を制御する。液冷媒制御弁ＶＬはＯＮ／ＯＦＦ式でも良いし、開度を連続的に制御できるものでも良い。
ターボ冷凍機の負荷が所定の値よりも小さいときには、液冷媒制御弁ＶＬを閉じ、電動機１２をガス冷媒のみで冷却する。ここで、所定の値とは、モータのコイル温度が例えば８０℃を超えることがないような負荷で、実験的に求めるとよい。
負荷の検出は、例えば電動機に設けた温度センサの値をもとにする。他に、電流値やベーン開度、冷水温度差など、負荷状態に相関する物理量でも良い。これにより、電動機の冷却効果を落とすことなく、液冷媒の散布量を減らすことができる。液冷媒の排出量が減少し、冷凍機の効率が向上する。
３）ガス冷媒の流量調整
ｉ）上記２）と同様に、ガス冷媒供給配管６にも制御弁ＶＧを設け、負荷に応じてガス冷媒の流量を制御する。冷却用のガス冷媒を減らすことで、圧縮機の仕事が減少し、結果として冷凍機の効率が向上する。
ターボ冷凍機の負荷が所定の値よりも大きいときには、ガス冷媒流量が１００％になるようにガス冷媒制御弁ＶＧを制御し、さらに、前記液冷媒制御弁ＶＬを前記負荷に応じて制御する。ここで、所定の値とは、モータのコイル温度が例えば８０℃を超えることがないような負荷で、実験的に求めるとよい。
ii）また、冷凍機の負荷が小さい時はホットガスバイパスが広く実施されている。これは凝縮器の冷媒ガスを蒸発器に流入させて冷凍機の低負荷絞りに対応するものである。通常はホットガスバイパス用の配管と制御弁を設ける必要がある。
図２に示すように、ガス冷媒供給配管６に制御弁ＶＧを設けることで、これをホットガスバイパスと兼用することができる。極低負荷時に制御弁ＶＧを開く制御を行うことで、冷凍機を低負荷まで絞ることができる。 Next, a method for cooling the electric motor 12 of the turbo compressor 1 in the turbo refrigerator having the configuration shown in FIG. 2 will be described.
1) Cooling by combined use of liquid refrigerant and gas refrigerant i) Although the present invention is directed to a turbo refrigerator having an economizer, the economizer may be omitted. Generally, an electric motor of a turbo refrigerator is cooled by a liquid refrigerant. The liquid refrigerant evaporates with the heat of the electric motor, and mainly cools the electric motor with its latent heat.
The liquid refrigerant is supplied from the condenser 2 to the electric motor 12 by the refrigerant pump 9. Since the pressure relationship is evaporator ≦ electric motor ≦ condenser, there is no need for the refrigerant pump. The evaporated gas is discharged toward the evaporator 3 having a low pressure. It can also discharge | emit to the condenser 2 and the economizer 4 (refer FIG. 1).
ii) It is technically difficult to distribute the liquid refrigerant uniformly inside the motor and evaporate all of it. Actually, several times the required amount of liquid refrigerant is dispersed in the electric motor 12. The unevaporated liquid refrigerant is discharged from the lower part of the electric motor 12 toward the evaporator 3. Since this liquid refrigerant does not go through the economizer, it causes a loss and reduces the efficiency of the refrigerator.
iii) On the other hand, when the electric motor 12 is cooled with a gas refrigerant, the liquid refrigerant is not discharged. Since the gas refrigerant has a small specific heat, a large flow rate is required to cool all the calorific value of the electric motor. A large-diameter gas passage for supplying a large amount of gas is required. The temperature distribution in the electric motor is not uniform, and a portion where current flows, such as a coil, generates heat and becomes high temperature.
iv) Therefore, in the present invention, the liquid refrigerant is sprayed toward the high temperature portion of the electric motor to effectively perform cooling. Moreover, the whole is cooled with a gas refrigerant by providing an inflow passage for the gas refrigerant. Thereby, the spraying amount of the liquid refrigerant can be reduced without reducing the cooling effect of the electric motor 12. The amount of liquid refrigerant discharged is reduced and the efficiency of the refrigerator is improved.
2) When the load on the motor is small, cooling with only the gas refrigerant i) The load on the refrigerator and the amount of heat generated by the motor are correlated. When the load on the refrigerator is high, it generates a lot of heat. When the load is low, the calorific value is small. Throughout the year, refrigerators are overwhelmingly long operating at low loads. When the load is low, the amount of heat generated by the motor is small, so cooling can be achieved even if the amount of liquid refrigerant sprayed is reduced. Furthermore, depending on the conditions, it is possible to cool the liquid refrigerant alone by stopping the spraying of the liquid refrigerant.
ii) Therefore, in the present invention, the liquid refrigerant supply pipe 7 is provided with a liquid refrigerant control valve V L to control the amount of liquid refrigerant sprayed according to the load. The liquid refrigerant control valve VL may be an ON / OFF type or a valve capable of continuously controlling the opening degree.
When the load of the turbo refrigerator is smaller than a predetermined value, the liquid refrigerant control valve VL is closed and the electric motor 12 is cooled only with the gas refrigerant. Here, the predetermined value may be experimentally obtained with a load such that the coil temperature of the motor does not exceed 80 ° C., for example.
For example, the load is detected based on the value of a temperature sensor provided in the electric motor. In addition, a physical quantity correlated with a load state such as a current value, a vane opening degree, or a cold water temperature difference may be used. Thereby, the spraying amount of the liquid refrigerant can be reduced without reducing the cooling effect of the electric motor. The amount of liquid refrigerant discharged is reduced and the efficiency of the refrigerator is improved.
3) Like the flow rate adjusting i) above 2) of gas refrigerant, the control valve V G provided in the gas refrigerant supply pipe 6, to control the flow rate of the gas refrigerant in accordance with the load. By reducing the gas refrigerant for cooling, the work of the compressor is reduced, and as a result, the efficiency of the refrigerator is improved.
When the load of the turbo chiller is greater than a predetermined value, it controls the gas refrigerant control valve V G so that the gas refrigerant flow rate is 100%, further controlled in accordance with the liquid refrigerant control valve V L to the load To do. Here, the predetermined value may be experimentally obtained with a load such that the coil temperature of the motor does not exceed 80 ° C., for example.
ii) Hot gas bypass is widely implemented when the load on the refrigerator is small. This corresponds to the low load throttling of the refrigerator by allowing the refrigerant gas of the condenser to flow into the evaporator. Normally, it is necessary to provide piping and a control valve for hot gas bypass.
As shown in FIG. 2, by providing the control valve V G to the gas refrigerant supply pipe 6, which can be also used as the hot gas bypass. By performing the control to open the control valve V G during extremely low load, it is possible to narrow the refrigerator to a low load.

図３は、図１に示すターボ冷凍機の負荷を判定する構成を示す模式図である。
１）冷水の温度による判定
図３に示すように、蒸発器３には、冷水入口温度を測定する温度センサＴ１と、冷水出口温度を測定する温度センサＴ２とが設置されている。すなわち、温度センサＴ１により蒸発器３内の冷媒と熱交換する冷水の入口温度を測定し、温度センサＴ２により蒸発器３内の冷媒と熱交換した後の冷水の出口温度を測定するようになっている。温度センサＴ１および温度センサＴ２は、それぞれ制御装置１０に接続されている。これにより、制御装置１０において、冷水入口温度と冷水出口温度との温度差と、定格（固定）の冷水流量とから冷凍能力Ｑｅを算出することができるようになっている。蒸発器３を流れる冷水流量が変流量である場合には、図３に示すように、冷水出口配管に冷水流量を計測する流量センサＦＥを設けることにより、冷水入口温度と冷水出口温度との温度差と、流量センサＦＥで計測した冷水流量とを乗算することにより冷凍能力Ｑｅを算出することができる。 FIG. 3 is a schematic diagram showing a configuration for determining the load of the turbo refrigerator shown in FIG.
1) Judgment by Temperature of Cold Water As shown in FIG. 3, the evaporator 3 is provided with a temperature sensor T1 for measuring the cold water inlet temperature and a temperature sensor T2 for measuring the cold water outlet temperature. That is, the temperature sensor T1 measures the inlet temperature of cold water that exchanges heat with the refrigerant in the evaporator 3, and the temperature sensor T2 measures the outlet temperature of cold water after heat exchange with the refrigerant in the evaporator 3. ing. The temperature sensor T1 and the temperature sensor T2 are connected to the control device 10, respectively. Thereby, in the control apparatus 10, the refrigerating capacity Qe can be calculated from the temperature difference between the cold water inlet temperature and the cold water outlet temperature and the rated (fixed) cold water flow rate. When the flow rate of the cold water flowing through the evaporator 3 is a variable flow rate, as shown in FIG. 3, by providing a flow rate sensor FE for measuring the flow rate of the cold water in the cold water outlet pipe, the temperature between the cold water inlet temperature and the cold water outlet temperature. The refrigeration capacity Qe can be calculated by multiplying the difference by the cold water flow rate measured by the flow rate sensor FE.

なお、図３に示すように、冷水入口配管と冷水出口配管との間に差圧計ΔＰｅを設けて蒸発器３で生ずる冷水圧力損失を計測し、蒸発器３の冷水圧力損失から蒸発器３を流れる冷水流量を推算し、推算した冷水流量に、冷水入口温度と冷水出口温度との温度差を乗算することにより冷凍能力Ｑｅを算出してもよい。
このように、制御装置１０は、冷凍能力Ｑｅを算出することにより、ターボ冷凍機が低負荷であるか高負荷であるかを判断し、高負荷の場合にはガス冷媒と液冷媒とを併用して電動機１２を冷却し、低負荷の場合には電動機１２をガス冷媒と少量の液冷媒で、またはガス冷媒のみで冷却する。 As shown in FIG. 3, a differential pressure gauge ΔPe is provided between the cold water inlet pipe and the cold water outlet pipe to measure the cold water pressure loss generated in the evaporator 3, and the evaporator 3 is determined from the cold water pressure loss of the evaporator 3. The refrigeration capacity Qe may be calculated by estimating the flowing cold water flow rate and multiplying the estimated cold water flow rate by the temperature difference between the cold water inlet temperature and the cold water outlet temperature.
In this way, the control device 10 determines whether the turbo chiller has a low load or a high load by calculating the refrigeration capacity Qe, and in the case of a high load, the gas refrigerant and the liquid refrigerant are used in combination. Then, the electric motor 12 is cooled, and when the load is low, the electric motor 12 is cooled with a gas refrigerant and a small amount of liquid refrigerant, or only with the gas refrigerant.

２）電動機内部の温度による判定
図３に示すように、電動機１２には、電動機内部の温度を測定する温度センサＴ３が設置されている。温度センサＴ３は、例えば、熱電対を用い、温度センサの検出端は電動機内部で最も高温になる部分の温度が測定できるようになっている。温度センサＴ３は、制御装置１０に接続されている。ターボ冷凍機の稼働中に温度センサＴ３により電動機１２の内部の温度を測定する。制御装置１０は、温度センサＴ３の測定信号に基づいてターボ冷凍機が低負荷であるか高負荷であるかを判断し、高負荷の場合にはガス冷媒と液冷媒とを併用して電動機１２を冷却し、低負荷の場合には電動機１２をガス冷媒と少量の液冷媒で、またはガス冷媒のみで冷却する。 2) Determination based on the temperature inside the motor As shown in FIG. 3, the motor 12 is provided with a temperature sensor T <b> 3 that measures the temperature inside the motor. The temperature sensor T3 uses, for example, a thermocouple, and the detection end of the temperature sensor can measure the temperature at the highest temperature in the electric motor. The temperature sensor T3 is connected to the control device 10. During the operation of the turbo refrigerator, the temperature inside the electric motor 12 is measured by the temperature sensor T3. The control device 10 determines whether the turbo chiller has a low load or a high load based on the measurement signal of the temperature sensor T3, and in the case of a high load, the electric motor 12 uses a combination of gas refrigerant and liquid refrigerant. In the case of a low load, the motor 12 is cooled with a gas refrigerant and a small amount of liquid refrigerant, or only with a gas refrigerant.

図４は、電動機１２を冷却した後の冷媒を蒸発器３に戻すための構成を示す模式図である。
図２に示す電動機を冷却する構成において、液冷媒を用いて電動機１２を冷却した場合、液冷媒の多くは蒸発してガスになるが、蒸発しきれないで残った液冷媒は電動機１２の底部に溜まる。そこで、本発明においては、図４に示すように、電動機１２から排出されるガス冷媒を駆動用ガスとして、電動機１２に溜まっている液冷媒を吸引して該液冷媒を電動機１２から排出するためのエジェクタ１５を設けている。ガス冷媒を電動機１２からエジェクタ１５に導くガス冷媒排出配管１６は、電動機１２の上部側に接続されている。液冷媒を電動機１２から吸引するための液冷媒排出配管１７は、電動機１２の底部側に接続されている。エジェクタ１５の吐出側は蒸発器３に接続されている。 FIG. 4 is a schematic diagram showing a configuration for returning the refrigerant after cooling the electric motor 12 to the evaporator 3.
In the configuration for cooling the electric motor shown in FIG. 2, when the electric motor 12 is cooled using liquid refrigerant, most of the liquid refrigerant evaporates into gas, but the liquid refrigerant remaining without being evaporated is the bottom of the electric motor 12. Accumulate. Therefore, in the present invention, as shown in FIG. 4, the gas refrigerant discharged from the electric motor 12 is used as a driving gas, the liquid refrigerant accumulated in the electric motor 12 is sucked and the liquid refrigerant is discharged from the electric motor 12. The ejector 15 is provided. A gas refrigerant discharge pipe 16 that guides the gas refrigerant from the electric motor 12 to the ejector 15 is connected to the upper side of the electric motor 12. A liquid refrigerant discharge pipe 17 for sucking the liquid refrigerant from the electric motor 12 is connected to the bottom side of the electric motor 12. The discharge side of the ejector 15 is connected to the evaporator 3.

図４に示す構成において、電動機１２から排出されるガス冷媒はガス冷媒排出配管１６を介してエジェクタ１５に供給される。エジェクタ１５に供給されるガス冷媒は、所定の圧力を持っているため、エジェクタ１５を駆動する駆動用ガスとして機能し、エジェクタ１５内に負圧が形成される。そのため、電動機１２に溜まっている液冷媒は、エジェクタ１５に吸引されるため電動機１２から排出される。エジェクタ１５で合流したガス冷媒と液冷媒は、エジェクタ１５の吐出側から１本の配管で蒸発器３に戻すことができる。   In the configuration shown in FIG. 4, the gas refrigerant discharged from the electric motor 12 is supplied to the ejector 15 through the gas refrigerant discharge pipe 16. Since the gas refrigerant supplied to the ejector 15 has a predetermined pressure, it functions as a driving gas for driving the ejector 15, and a negative pressure is formed in the ejector 15. Therefore, the liquid refrigerant accumulated in the electric motor 12 is discharged from the electric motor 12 because it is sucked into the ejector 15. The gas refrigerant and the liquid refrigerant merged in the ejector 15 can be returned to the evaporator 3 from the discharge side of the ejector 15 through one pipe.

これまで本発明の実施形態について説明したが、本発明は上述の実施形態に限定されず、その技術思想の範囲内において、種々の異なる形態で実施されてよいことは勿論である。   Although the embodiment of the present invention has been described so far, the present invention is not limited to the above-described embodiment, and it is needless to say that the present invention may be implemented in various different forms within the scope of the technical idea.

１ ターボ圧縮機
２ 凝縮器
３ 蒸発器
４ エコノマイザ
５ 冷媒配管
６ ガス冷媒供給配管
７ 液冷媒供給配管
８ 冷却冷媒戻り配管
９ 冷媒ポンプ
１０ 制御装置
１２ 電動機
１５ エジェクタ
１６ ガス冷媒排出配管
１７ 液冷媒排出配管
Ｔ１，Ｔ２，Ｔ３ 温度センサ
ＦＥ 流量センサ DESCRIPTION OF SYMBOLS 1 Turbo compressor 2 Condenser 3 Evaporator 4 Economizer 5 Refrigerant piping 6 Gas refrigerant supply piping 7 Liquid refrigerant supply piping 8 Cooling refrigerant return piping 9 Refrigerant pump 10 Controller 12 Electric motor 15 Ejector 16 Gas refrigerant discharge piping 17 Liquid refrigerant discharge piping T1, T2, T3 Temperature sensor FE Flow sensor

Claims (6)

冷水から熱を奪って冷媒が蒸発し冷凍効果を発揮する蒸発器と、冷媒を羽根車によって圧縮するターボ圧縮機と、ターボ圧縮機を駆動する電動機と、圧縮された冷媒を冷却水で冷却して凝縮させる凝縮器とを備えたターボ冷凍機において、
前記凝縮器から前記電動機にガス冷媒を供給するガス冷媒供給配管と、
前記凝縮器から前記電動機に液冷媒を供給する液冷媒供給配管とを備え、
前記電動機をガス冷媒と液冷媒とを併用して冷却するようにしたことを特徴とするターボ冷凍機。 An evaporator that draws heat from cold water and evaporates the refrigerant to exert a refrigeration effect, a turbo compressor that compresses the refrigerant with an impeller, an electric motor that drives the turbo compressor, and the compressed refrigerant is cooled with cooling water In a centrifugal chiller equipped with a condenser for condensing
A gas refrigerant supply pipe for supplying a gas refrigerant from the condenser to the electric motor;
A liquid refrigerant supply pipe for supplying liquid refrigerant from the condenser to the electric motor,
A turbo refrigerator, wherein the electric motor is cooled by using a gas refrigerant and a liquid refrigerant in combination. 前記液冷媒供給配管に設置される液冷媒制御弁と、冷凍負荷を検出する手段を備え、
ターボ冷凍機の負荷が所定の値よりも小さいときには、前記液冷媒制御弁を閉じ、前記電動機をガス冷媒のみで冷却するようにしたことを特徴とする請求項１記載のターボ冷凍機。 A liquid refrigerant control valve installed in the liquid refrigerant supply pipe, and means for detecting a refrigeration load,
2. The turbo chiller according to claim 1, wherein when the load of the turbo chiller is smaller than a predetermined value, the liquid refrigerant control valve is closed and the electric motor is cooled only by a gas refrigerant. 前記ガス冷媒供給配管に設置されるガス冷媒制御弁と、冷凍負荷を検出する手段を備え、前記ガス冷媒制御弁を負荷に応じて開度制御することを特徴とする請求項２記載のターボ冷凍機。   The turbo refrigeration according to claim 2, further comprising a gas refrigerant control valve installed in the gas refrigerant supply pipe and means for detecting a refrigeration load, wherein the opening degree of the gas refrigerant control valve is controlled according to the load. Machine. ターボ冷凍機の負荷が所定の値よりも大きいときには、ガス冷媒流量が１００％になるように前記ガス冷媒制御弁を制御し、さらに、前記液冷媒制御弁を前記負荷に応じて制御することを特徴とする請求項１乃至３のいずれか一項に記載のターボ冷凍機。   When the load of the turbo chiller is larger than a predetermined value, the gas refrigerant control valve is controlled so that the gas refrigerant flow rate becomes 100%, and further the liquid refrigerant control valve is controlled according to the load. The turbo refrigerator as described in any one of Claims 1 thru | or 3 characterized by the above-mentioned. 負荷が小さい場合に、前記制御弁をホットガスバイパス制御に使用することを特徴とする請求項１乃至４のいずれか一項に記載のターボ冷凍機。   The turbo chiller according to any one of claims 1 to 4, wherein the control valve is used for hot gas bypass control when the load is small. 前記電動機から排出されるガス冷媒を駆動用ガスとして、前記電動機に溜まっている液冷媒を吸引して該液冷媒を電動機から排出するためのエジェクタを設け、前記エジェクタにより吸引された液冷媒は、前記蒸発器に戻されることを特徴とする請求項１乃至５のいずれか一項に記載のターボ冷凍機。   A gas refrigerant discharged from the electric motor is used as a driving gas, an ejector for sucking the liquid refrigerant accumulated in the electric motor and discharging the liquid refrigerant from the electric motor is provided, and the liquid refrigerant sucked by the ejector is: The centrifugal chiller according to any one of claims 1 to 5, wherein the centrifugal chiller is returned to the evaporator.
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