JPH1163688A - Method of setting refrigerant evaporation pressure corresponding to load of freezing equipment - Google Patents
Method of setting refrigerant evaporation pressure corresponding to load of freezing equipmentInfo
- Publication number
- JPH1163688A JPH1163688A JP24212197A JP24212197A JPH1163688A JP H1163688 A JPH1163688 A JP H1163688A JP 24212197 A JP24212197 A JP 24212197A JP 24212197 A JP24212197 A JP 24212197A JP H1163688 A JPH1163688 A JP H1163688A
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- evaporation
- pressure
- evaporation pressure
- refrigerant
- 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
Landscapes
- Air Conditioning Control Device (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】この発明は、冷媒の蒸発圧力
を調整することができる機能を有する冷凍設備におい
て、負荷に対応して冷媒の蒸発圧力を設定する方法に関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method for setting the evaporation pressure of a refrigerant in accordance with a load in a refrigeration facility having a function of adjusting the evaporation pressure of the refrigerant.
【0002】[0002]
【従来の技術】従来の冷凍設備には、冷媒の蒸発圧力を
調整する機能(EPR機能)を有するものがあり、この
蒸発圧力の調整は、冷凍設備が冷却しようとする設定温
度と、冷媒の蒸発温度との差Δtを図2に示すようなグ
ラフに基づいて各温度条件で予め固定し、設定温度すな
わち被冷却流体を冷却すべき温度からΔtを減じること
により冷媒の蒸発温度を求め、この蒸発温度に基づいて
使用冷媒の蒸気圧表(図示せず)を用いて冷媒蒸発圧力
を設定していた。2. Description of the Related Art Some conventional refrigeration systems have a function of adjusting the evaporating pressure of a refrigerant (EPR function). The difference Δt from the evaporation temperature is previously fixed under each temperature condition based on a graph as shown in FIG. 2, and the evaporation temperature of the refrigerant is obtained by subtracting Δt from the set temperature, that is, the temperature at which the fluid to be cooled is to be cooled. The refrigerant evaporation pressure has been set using a vapor pressure table (not shown) of the refrigerant used based on the evaporation temperature.
【0003】具体的には設定温度が−40℃であれば、
図2に示すグラフからΔtは3℃であるから求める蒸発
温度は−43℃となり、同様に設定温度が−10℃であ
ればΔtは5℃であるから蒸発温度は−15℃となる。[0003] Specifically, if the set temperature is -40 ° C,
Since Δt is 3 ° C. from the graph shown in FIG. 2, the required evaporation temperature is −43 ° C. Similarly, if the set temperature is −10 ° C., the Δt is 5 ° C., and the evaporation temperature is −15 ° C.
【0004】負荷が減少すると冷凍機の冷却出力を減少
させるが、設定温度が変わらなければ前述したようにΔ
tが固定されているので、蒸発温度は変わらない。した
がって被冷却流体たる例えば空気の吹き出し温度が下が
って過冷されるので、冷却後の空気を例えば電気ヒータ
等のヒータで加熱することにより設定温度を維持するよ
うにしていた。When the load decreases, the cooling output of the refrigerator decreases, but if the set temperature does not change, Δ
Since t is fixed, the evaporation temperature does not change. Therefore, since the temperature of the air to be cooled, for example, the air blowing temperature, is lowered and supercooled, the set temperature is maintained by heating the cooled air with a heater such as an electric heater.
【0005】[0005]
【発明が解決しようとする課題】しかし、上述した従来
の技術では冷凍設備が大きくなるに伴ってヒータの加熱
出力を大にしなければならず、したがってヒータに容量
の大なるものを使用しなければならず、いきおい設備コ
ストおよびランニングコストが高くなるという問題があ
る。However, in the prior art described above, the heating output of the heater must be increased as the size of the refrigeration equipment increases, and therefore, a heater having a large capacity must be used. In addition, there is a problem in that the equipment cost and running cost increase.
【0006】例えば最大3000m3/min の空気を循環
させる被冷却室に1000m3/minの対流風を流す場
合、被冷却室の内部に冷却対象物が少なくなって負荷が
減少し、3℃過冷されたとすると、 1000×60×1.2×0.24×3℃=51840
kcal/H よって51840÷860=60kwの加熱エネルギーを
ヒータによって出力する必要がある。For example, when convection air of 1000 m 3 / min is supplied to a cooled room for circulating a maximum of 3000 m 3 / min of air, the number of objects to be cooled is reduced inside the cooled room, and the load is reduced. If it is cooled, 1000 × 60 × 1.2 × 0.24 × 3 ° C. = 51840
kcal / H Therefore, 51840 ÷ 860 = 60 kW of heating energy needs to be output by the heater.
【0007】また、湿度制御を行う場合においても、負
荷が減少した際に蒸発温度が変わらないことから、被冷
却流体である空気が過冷されて過除湿を生じ、設定され
た湿度を維持するため加湿装置により加えられる加湿量
も多くなってしまい、加湿装置も容量の大なるものとし
なければならず、これまた設備コストおよびランニング
コストが高くなるという問題もある。Further, even when humidity control is performed, since the evaporation temperature does not change when the load is reduced, the air to be cooled is supercooled to cause excessive dehumidification, and the set humidity is maintained. Therefore, the amount of humidification added by the humidifier also increases, and the capacity of the humidifier must also be increased, and there is also a problem that equipment costs and running costs increase.
【0008】[0008]
【本発明の目的】本発明は以上の問題点を解決するため
になされたもので、ヒータや加湿装置を容量の小なるも
のとすることができて設備コストおよびランニングコス
トの安い冷媒蒸発圧力設定方法および冷凍設備を提供す
ることを目的とする。SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and can reduce the capacity of a heater and a humidifier so that the equipment pressure and the running cost can be reduced. It is an object to provide a method and a refrigeration facility.
【0009】[0009]
【課題を解決するための手段】以上の目的を達成するた
めに、請求項1の発明は、冷媒の蒸発圧力を調整する機
能を有する冷凍設備の冷媒蒸発圧力設定方法において、
被冷却流体の温度調節用設定温度T1 、被冷却流体の温
度TA から現在の蒸発温度TE を引いた値または設定温
度により固定した値ΔT、0より大きく1以下の値をと
る係数Y、冷凍機の冷却出力の百分率Xから、蒸発圧力
調整用蒸発温度Tを、 T=T1 −ΔT{1−Y(100−X)/100} により演算し、同蒸発圧力調節用設定温度Tから使用冷
媒の蒸気圧表を用いて蒸発圧力を設定することを特徴と
する冷凍設備の負荷に対応する冷媒蒸発圧力設定方法で
ある。In order to achieve the above object, a first aspect of the present invention is a method of setting a refrigerant evaporation pressure of a refrigeration facility having a function of adjusting a refrigerant evaporation pressure.
Temperature control set temperature T 1 of the fluid to be cooled, the coefficient takes the current evaporation temperature T E to a value obtained by subtracting or setting temperature by a fixed value [Delta] T, greater value of 1 or less than 0 from the temperature T A of the cooling fluid Y From the cooling output percentage X of the refrigerator, an evaporation temperature T for evaporating pressure adjustment is calculated by T = T 1 −ΔT {1-Y (100−X) / 100}, and the set temperature T for evaporating pressure adjustment is calculated. A method for setting a refrigerant evaporating pressure corresponding to a load of a refrigeration facility, wherein the evaporating pressure is set using a vapor pressure table of a used refrigerant.
【0010】また、請求項2の発明は、冷凍機と蒸発器
との間の冷媒管に蒸発器内の蒸発圧力を制御するための
コントロール弁を備えるとともに、被冷却流体の温度T
A を検知する温度センサを備え、被冷却流体の温度調節
用設定温度T1 、被冷却流体の温度TA から現在の蒸発
温度TE を引いた値または設定温度により固定した値Δ
T、0より大きく1以下の値をとる係数Y、冷凍機の冷
却出力の百分率Xから、蒸発圧力調整用蒸発温度Tを、 T=T1 −ΔT{1−Y(100−X)/100} により演算し、さらに同蒸発圧力調節用設定温度Tから
使用冷媒の蒸気圧表を用いて蒸発圧力を演算する演算器
を備え、同演算器から出力される蒸発圧力設定信号によ
り前記コントロール弁の開度が調節されて蒸発圧力が設
定されることを特徴とする冷凍設備である。Further, according to the present invention, the refrigerant pipe between the refrigerator and the evaporator is provided with a control valve for controlling the evaporating pressure in the evaporator and the temperature T of the fluid to be cooled.
A temperature sensor for detecting the A, setting temperature adjustment of the cooling fluid temperature T 1, the value Δ fixed by the value or the set temperature minus the current evaporation temperature T E of the temperature T A of the cooling fluid
From T, coefficient Y that takes a value greater than 0 and 1 or less, and percentage X of the cooling output of the refrigerator, the evaporation temperature T for adjusting the evaporation pressure is calculated as follows: T = T 1 −ΔT {1−Y (100−X) / 100演算, and a calculator for calculating the evaporation pressure using the vapor pressure table of the refrigerant to be used from the set temperature T for adjusting the evaporation pressure, and the control valve of the control valve is controlled by the evaporation pressure setting signal output from the calculator. A refrigeration facility characterized in that the opening degree is adjusted and the evaporation pressure is set.
【0011】[0011]
【発明の実施の形態】本発明の一実施形態を、図1を用
いて説明する。この実施形態に係る冷凍設備は被冷却流
体を空気とし、被冷却室たる例えば低温環境試験室等の
試験室1内を冷却するものとしてあり、この冷凍設備に
おいては冷凍機2からの冷媒往管3が蒸発器4の冷媒入
口に接続され、同蒸発器の冷媒出口からの冷媒復管5が
冷凍機に接続されている。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described with reference to FIG. The refrigeration equipment according to this embodiment uses a fluid to be cooled as air, and cools the inside of a test chamber 1 such as a low-temperature environment test chamber, which is a cooled chamber. 3 is connected to the refrigerant inlet of the evaporator 4, and the refrigerant return pipe 5 from the refrigerant outlet of the evaporator is connected to the refrigerator.
【0012】蒸発器4は空調機6の熱交換器7へ冷ブラ
インを送るものとしてあって、蒸発器4のブライン出口
はブラインポンプ8を備えるブライン往管9により熱交
換器7の流入口に接続され、また熱交換器7の流出口は
ブライン復管10により蒸発器4のブライン入口に接続
されている。The evaporator 4 sends cold brine to the heat exchanger 7 of the air conditioner 6, and the brine outlet of the evaporator 4 is connected to the inlet of the heat exchanger 7 by a brine forward pipe 9 having a brine pump 8. The outlet of the heat exchanger 7 is connected to the brine inlet of the evaporator 4 by a brine return pipe 10.
【0013】空調機6内には熱交換器7の上流側に送風
機11が設けられ、また下流側には電気ヒータ12およ
び加湿器21が設けられており、空調機は空気往路13
および空気復路14により試験室1に接続されていて、
前記送風機11の駆動により試験室1内の空気は空気復
路14から空調機内に送られて熱交換器7により冷却さ
れ、電気ヒータ12によって加熱され、さらに加湿器2
1で所要の湿度に加湿された後、空気往路13により試
験室1に戻される。In the air conditioner 6, a blower 11 is provided on the upstream side of the heat exchanger 7, and an electric heater 12 and a humidifier 21 are provided on the downstream side.
And connected to the test chamber 1 by the air return path 14,
By driving the blower 11, the air in the test chamber 1 is sent from the air return path 14 into the air conditioner, cooled by the heat exchanger 7, heated by the electric heater 12, and further cooled by the humidifier 2.
After being humidified to the required humidity in step 1, it is returned to the test room 1 by way of the outward air path 13.
【0014】空気往路13の吹出口には温度センサ15
が設けられ、空気温度すなわち被冷却流体の温度TA が
検知されて温度調節計16に送られる。温度調節計16
は図示しない入力手段を有し、任意の設定温度T1 (吹
出口における空気の温度調節用設定温度)が設定され、
この温度調節計は被冷却流体の温度TA と設定温度T1
の差に基づいて冷凍機2へ冷却出力設定信号を発し、こ
の冷却出力設定信号による冷却出力値は冷却出力の百分
率Xとして、前記被冷却流体の温度TA および設定温度
T1 とともに演算器17へ出力される。A temperature sensor 15 is provided at the outlet of the air outward path 13.
Is provided, and the air temperature, that is, the temperature T A of the fluid to be cooled is detected and sent to the temperature controller 16. Temperature controller 16
Has input means (not shown) for setting an arbitrary set temperature T 1 (set temperature for adjusting the temperature of air at the outlet),
This temperature controller has a temperature T A of the fluid to be cooled and a set temperature T 1.
A cooling output setting signal is sent to the refrigerator 2 based on the difference between the cooling fluid and the cooling output value according to the cooling output setting signal as a percentage X of the cooling output together with the temperature T A of the fluid to be cooled and the set temperature T 1. Output to
【0015】上述した各データを演算器17において次
の(A) 式により演算することで、蒸発器4における次回
の蒸発温度が求められる。The next data of the evaporator 4 in the evaporator 4 is obtained by calculating the above-mentioned data in the calculator 17 according to the following equation (A).
【0016】 T=T1 −ΔT{1−Y(100−X)/100}・・(A) T :次回の蒸発温度 T1 :設定温度 ΔT:被冷却流体の温度TA −現在の蒸発温度TE Y :予め設定された0より大きく1以下の係数 X :冷凍機の冷却出力(%) なお、上式(A) における係数Yは冷却出力Xが0となっ
た場合にT=T1 となって冷却できなくなるのを防止す
るためであり、冷凍設備の規模等により適宜決定する
が、例えばY=0.9とする。また、現在の蒸発温度T
E は蒸発器内の温度を直接検知するのではなく、現在の
蒸発圧力の設定用に演算された前回の蒸発温度を代入す
る。T = T 1 −ΔT {1−Y (100−X) / 100} (A) T: Next evaporation temperature T 1 : Set temperature ΔT: Temperature of the fluid to be cooled T A −Current evaporation temperature T E Y: preset more than 0 to less than 1 factor X: cooling output of the refrigerator (%) Note, T = T if the coefficient in the above formula (a) Y became the cooling output X is 0 This is to prevent the cooling from becoming 1 and being unable to be performed, and is appropriately determined according to the scale of the refrigeration equipment, etc., for example, Y = 0.9. Also, the current evaporation temperature T
E does not directly detect the temperature in the evaporator, but substitutes the previous evaporation temperature calculated for setting the current evaporation pressure.
【0017】演算器17での演算結果たる次回の蒸発温
度Tは使用冷媒の図示しない蒸気圧表を用いて蒸発圧力
に換算され、蒸発圧力の調整(EPR)の制御を行う圧
力制御装置18へ蒸発圧力設定信号(ERP設定信号)
として送られ、圧力制御装置18ではEPR設定信号と
圧力センサ18aで検知された蒸発圧力に基づいて冷媒
復管5に設けられたコントロール弁19の弁開度を調整
し、これにより冷媒の次回の蒸発圧力が設定される。The next evaporation temperature T calculated by the arithmetic unit 17 is converted into an evaporation pressure using a vapor pressure table (not shown) of the refrigerant to be used, and is sent to a pressure control device 18 for controlling the adjustment (EPR) of the evaporation pressure. Evaporation pressure setting signal (ERP setting signal)
The pressure control device 18 adjusts the valve opening of the control valve 19 provided in the refrigerant return pipe 5 based on the EPR setting signal and the evaporation pressure detected by the pressure sensor 18a. The evaporation pressure is set.
【0018】また、前記式によって蒸発温度が演算され
た結果に基づいて冷媒蒸発圧力が設定されても、空気吹
き出し温度の若干の低下は生じ得るので、この低下をカ
バーするために温度調節計16は電気ヒータ12の加熱
出力を定める加熱出力設定信号を発し、同信号は加熱制
御装置20に送られて電気ヒータ12の加熱出力が制御
される。Further, even if the refrigerant evaporation pressure is set based on the result of calculating the evaporation temperature by the above equation, a slight decrease in the air blowing temperature may occur. Generates a heating output setting signal that determines the heating output of the electric heater 12, and the signal is sent to the heating control device 20 to control the heating output of the electric heater 12.
【0019】以上の実施形態においては前記式(A) の係
数Yは0.9であったが、他の実施形態においては0.
9よりも若干小さいかまたは大きい値を取ることが可能
である。すなわち0より大きく1以下の値であれば、こ
の発明の効果を得ることが可能である。In the above embodiment, the coefficient Y in the equation (A) is 0.9, but in other embodiments, the coefficient Y is equal to 0.9.
Values slightly smaller or larger than 9 are possible. That is, if the value is larger than 0 and equal to or smaller than 1, the effect of the present invention can be obtained.
【0020】また、前記式(A) においてはΔTを被冷却
流体の温度から現在の蒸発温度を減じた値としている
が、このΔTは図2に示す値Δtを用いてもよく、この
場合にも上述した本実施形態とほぼ同様の過冷防止の効
果を得ることができる。In the above equation (A), ΔT is a value obtained by subtracting the current evaporation temperature from the temperature of the fluid to be cooled. However, ΔT may be the value Δt shown in FIG. The same effect of preventing overcooling as in the above-described embodiment can be obtained.
【0021】さらに、上述した実施形態では蒸発器4に
おいて冷却したブラインをブラインポンプ8によって空
調機6内の熱交換器7に送るようにしているが、空調機
内に蒸発器を設け、この蒸発器に冷凍機2からの冷媒を
直接送るようにしてもよい。Further, in the above-described embodiment, the brine cooled in the evaporator 4 is sent to the heat exchanger 7 in the air conditioner 6 by the brine pump 8, but an evaporator is provided in the air conditioner and this evaporator is provided. The refrigerant from the refrigerator 2 may be directly sent to the refrigerator.
【0022】また、上述した実施形態ではヒータに電気
ヒータ12を使用しているが、加熱出力を制御すること
ができるものであれば、他のヒータを用いることもでき
る。In the above-described embodiment, the electric heater 12 is used as the heater. However, another heater can be used as long as the heating output can be controlled.
【0023】さらに、上述した実施形態では蒸発温度T
E を現在の圧力設定用に用いられた蒸発温度としている
が、圧力センサ18aで検知される圧力に基づいて使用
冷媒の蒸気圧表から換算したり、あるいは圧力センサと
は別に蒸発器4に蒸発温度を検知する温度センサを設け
て実際の蒸発温度を検知してもよい。また、上述した実
施形態では空調機6内に加湿器21を設けてあるが、加
湿器を設けない場合もある。Further, in the above embodiment, the evaporation temperature T
E is the evaporating temperature used for the current pressure setting, but is converted from the vapor pressure table of the refrigerant used based on the pressure detected by the pressure sensor 18a, or evaporates to the evaporator 4 separately from the pressure sensor. A temperature sensor for detecting the temperature may be provided to detect the actual evaporation temperature. Although the humidifier 21 is provided in the air conditioner 6 in the above-described embodiment, the humidifier may not be provided in some cases.
【0024】[0024]
【発明の作用、効果】以上説明したように、この実施形
態によれば、負荷が減少し冷凍機の冷却出力の百分率X
が小さくなると、蒸発温度を演算するための前記(A) 式
の{ }内の値が小さくなり、したがって蒸発温度が設
定温度に近づく。As described above, according to this embodiment, the load is reduced and the cooling output percentage X of the refrigerator is reduced.
Is smaller, the value in the parentheses in the above equation (A) for calculating the evaporation temperature becomes smaller, and therefore the evaporation temperature approaches the set temperature.
【0025】これにより空気の吹き出し温度の不必要な
低下(過冷)が防止され、したがってヒータを容量の小
なるものとすることができ、省エネ効果を得ることがで
きる。As a result, unnecessary lowering (supercooling) of the air blowing temperature is prevented, so that the capacity of the heater can be reduced, and an energy saving effect can be obtained.
【0026】また、過冷に伴う過除湿を防止するために
設けられる加湿器も過冷が殆どなくなるので、容量の小
なるものとすることができて、このことからも省エネ効
果を得ることができる。Further, since the humidifier provided for preventing the excessive dehumidification accompanying the supercooling hardly undergoes the supercooling, the capacity can be reduced, and the energy saving effect can be obtained from this. it can.
【図1】本発明の一実施形態に係る冷凍設備の概略回路
図。FIG. 1 is a schematic circuit diagram of a refrigeration facility according to one embodiment of the present invention.
【図2】従来の技術において冷媒蒸発圧力を設定するた
めの冷媒の蒸発温度を求めるのに用いられたグラフ。FIG. 2 is a graph used to determine a refrigerant evaporation temperature for setting a refrigerant evaporation pressure in the related art.
1 試験室 2 冷凍機 4 蒸発器 6 空調機 7 熱交換器 11 送風機 12 電気ヒータ 15 温度センサ 16 温度調節計 17 演算器 18 圧力制御装置 19 コントロー
ル弁 20 加熱制御装置 21 加湿器DESCRIPTION OF SYMBOLS 1 Test room 2 Refrigerator 4 Evaporator 6 Air conditioner 7 Heat exchanger 11 Blower 12 Electric heater 15 Temperature sensor 16 Temperature controller 17 Computing unit 18 Pressure control device 19 Control valve 20 Heating control device 21 Humidifier
───────────────────────────────────────────────────── フロントページの続き (72)発明者 石井 正伸 神奈川県横浜市青葉区藤ケ丘1−50−4 コーポ飯田202号 (72)発明者 西原 正博 神奈川県横浜市緑区三保町1380−4 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Masanobu Ishii 1-50-4 Fujigaoka, Aoba-ku, Yokohama-shi, Kanagawa 202-Iida Corp. (72) Inventor Masahiro Nishihara 1380-4 Mihocho, Midori-ku, Yokohama-shi, Kanagawa
Claims (2)
凍設備の冷媒蒸発圧力設定方法において、被冷却流体の
温度調節用設定温度T1 、被冷却流体の温度TA から現
在の蒸発温度TE を引いた値または設定温度により固定
した値ΔT、0より大きく1以下の値をとる係数Y、冷
凍機の冷却出力の百分率Xから、蒸発圧力調整用蒸発温
度Tを、 T=T1 −ΔT{1−Y(100−X)/100} により演算し、同蒸発圧力調節用設定温度Tから使用冷
媒の蒸気圧表を用いて蒸発圧力を設定することを特徴と
する冷凍設備の負荷に対応する冷媒蒸発圧力設定方法。In a method for setting a refrigerant evaporation pressure of a refrigeration facility having a function of adjusting the evaporation pressure of a refrigerant, a set temperature T 1 for adjusting a temperature of a fluid to be cooled, a temperature T A of the fluid to be cooled, and a current evaporation temperature T A. From the value obtained by subtracting E or a value ΔT fixed by the set temperature, a coefficient Y that takes a value greater than 0 and equal to or less than 1 and a percentage X of the cooling output of the refrigerator, the evaporation temperature T for adjusting the evaporation pressure is given by: T = T 1 − ΔT {1−Y (100−X) / 100}, and the evaporation pressure is set using the vapor pressure table of the refrigerant used from the set temperature T for adjusting the evaporation pressure. Corresponding refrigerant evaporation pressure setting method.
の蒸発圧力を制御するためのコントロール弁を備えると
ともに、被冷却流体の温度TA を検知する温度センサを
備え、被冷却流体の温度調節用設定温度T1 、被冷却流
体の温度TA から現在の蒸発温度TE を引いた値または
設定温度により固定した値ΔT、0より大きく1以下の
値をとる係数Y、冷凍機の冷却出力の百分率Xから、蒸
発圧力調整用蒸発温度Tを、 T=T1 −ΔT{1−Y(100−X)/100} により演算し、さらに同蒸発圧力調節用設定温度Tから
使用冷媒の蒸気圧表を用いて蒸発圧力を演算する演算器
を備え、同演算器から出力される蒸発圧力設定信号によ
り前記コントロール弁の開度が調節されて蒸発圧力が設
定されることを特徴とする冷凍設備。2. A refrigerant pipe between a refrigerator and an evaporator is provided with a control valve for controlling an evaporation pressure in the evaporator, and a temperature sensor for detecting a temperature T A of a fluid to be cooled. setting temperature adjustment of the cooling fluid temperature T 1, the temperature T a value was fixed by the value or the set temperature minus the current evaporation temperature T E from ΔT of the cooling fluid, the coefficient takes a large value of 1 or less than 0 Y, From the percentage X of the cooling output of the refrigerator, the evaporation temperature T for adjusting the evaporation pressure is calculated by T = T 1 −ΔT {1-Y (100−X) / 100}, and the set temperature T for adjusting the evaporation pressure is further calculated. From the vapor pressure table of the refrigerant used, to calculate the evaporating pressure, and the evaporating pressure is set by adjusting the opening of the control valve by the evaporating pressure setting signal output from the operating device. Characterized refrigeration equipment.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP24212197A JP3418320B2 (en) | 1997-08-22 | 1997-08-22 | Method of setting refrigerant evaporation pressure corresponding to load of refrigeration equipment and refrigeration equipment |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP24212197A JP3418320B2 (en) | 1997-08-22 | 1997-08-22 | Method of setting refrigerant evaporation pressure corresponding to load of refrigeration equipment and refrigeration equipment |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH1163688A true JPH1163688A (en) | 1999-03-05 |
JP3418320B2 JP3418320B2 (en) | 2003-06-23 |
Family
ID=17084618
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP24212197A Expired - Lifetime JP3418320B2 (en) | 1997-08-22 | 1997-08-22 | Method of setting refrigerant evaporation pressure corresponding to load of refrigeration equipment and refrigeration equipment |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP3418320B2 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013148262A (en) * | 2012-01-19 | 2013-08-01 | Espec Corp | Environmental control apparatus |
-
1997
- 1997-08-22 JP JP24212197A patent/JP3418320B2/en not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2013148262A (en) * | 2012-01-19 | 2013-08-01 | Espec Corp | Environmental control apparatus |
Also Published As
Publication number | Publication date |
---|---|
JP3418320B2 (en) | 2003-06-23 |
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