JP3023637B2 - Refrigeration control method for constant temperature and humidity apparatus - Google Patents
Refrigeration control method for constant temperature and humidity apparatusInfo
- Publication number
- JP3023637B2 JP3023637B2 JP5137637A JP13763793A JP3023637B2 JP 3023637 B2 JP3023637 B2 JP 3023637B2 JP 5137637 A JP5137637 A JP 5137637A JP 13763793 A JP13763793 A JP 13763793A JP 3023637 B2 JP3023637 B2 JP 3023637B2
- Authority
- JP
- Japan
- Prior art keywords
- temperature
- refrigerant
- humidity
- room
- refrigerator
- 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.)
- Expired - Fee Related
Links
Classifications
-
- C—CHEMISTRY; METALLURGY
- C12—BIOCHEMISTRY; BEER; SPIRITS; WINE; VINEGAR; MICROBIOLOGY; ENZYMOLOGY; MUTATION OR GENETIC ENGINEERING
- C12M—APPARATUS FOR ENZYMOLOGY OR MICROBIOLOGY; APPARATUS FOR CULTURING MICROORGANISMS FOR PRODUCING BIOMASS, FOR GROWING CELLS OR FOR OBTAINING FERMENTATION OR METABOLIC PRODUCTS, i.e. BIOREACTORS OR FERMENTERS
- C12M41/00—Means for regulation, monitoring, measurement or control, e.g. flow regulation
- C12M41/12—Means for regulation, monitoring, measurement or control, e.g. flow regulation of temperature
- C12M41/14—Incubators; Climatic chambers
Landscapes
- Air Conditioning Control Device (AREA)
- Devices For Use In Laboratory Experiments (AREA)
Description
【産業上の利用分野】本発明は、恒温恒湿装置に係り、
特に装置室内の温度及び冷媒蒸発温度に応じて冷凍機の
圧縮機を回転数制御し、最適な冷却能力を供給して設定
された温湿度を安定維持するのに好適な恒温恒湿装置の
冷凍機制御方法及び冷凍機制御装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a thermo-hygrostat,
In particular, the refrigeration of a constant temperature and humidity device suitable for stably maintaining the set temperature and humidity by controlling the rotation speed of the compressor of the refrigerator in accordance with the temperature in the apparatus chamber and the refrigerant evaporation temperature and supplying the optimum cooling capacity. The present invention relates to a refrigerator control method and a refrigerator control device.
【従来の技術】従来の恒温恒湿装置の冷凍機制御方法に
おいては、冷凍サイクルの圧縮機に、回転数一定（固
定）のものを塔載し、冷却及び除湿能力を切換えるに
は、減圧機構及び蒸発器を２種以上並列に装備し、必要
に応じていずれか一方の減圧機構及び蒸発器に冷媒を流
すことにより、冷却能力の調整を行うのが一般的であ
り、この種の装置に関連する公知例として実開昭６３−
１３２２５２号公報がある。例えば半導体又は電子装置
等を試験する恒温恒湿装置は、基本性能として試験室の
到達可能な最低温度が決まっているが、この最低温度を
達成するには試験室最低温度に対し、適切な温度差以下
の冷凍サイクルの冷媒蒸発温度を維持する必要がある。
従来のように、冷凍サイクルの減圧機構にキャピラリチ
ューブ又は温度式膨張弁を用いると、装置周囲温度が高
い、すなわち空冷凝縮器による冷媒凝縮温度が高い場
合、冷媒蒸発温度も上昇して試験室最低温度の維持がで
きなくなり、設定した最低温度より上昇してしまう。し
かしこれを防ぐため、冷媒凝縮温度が高い場合でも、必
要な冷媒蒸発温度が得られるようにキャピラリチューブ
又は温度式膨張弁の減圧量を決定すると、周囲温度が低
く、冷媒凝縮温度が低い場合、冷媒蒸発温度が異常に低
下し冷凍機油温度低下による圧縮機損傷の原因となる。
従って、装置周囲温度の変化すなわち冷媒凝縮温度の変
化に対し影響を受けない冷媒蒸発温度を維持し、年間を
通して装置性能を一定に保つことがこの種の装置の重要
な条件である。2. Description of the Related Art In a conventional method for controlling a refrigerator of a constant temperature and humidity apparatus, a compressor having a fixed (fixed) rotation speed is mounted on a compressor of a refrigeration cycle, and a pressure reduction method is used to switch cooling and dehumidification capabilities. It is common to equip two or more types of mechanisms and evaporators in parallel, and to adjust the cooling capacity by flowing a refrigerant through one of the decompression mechanisms and the evaporator as necessary. As a well-known example related to
No. 132252. For example, the constant temperature and humidity equipment for testing semiconductors or electronic devices, etc., has a minimum temperature that the test room can reach as a basic performance, but to achieve this minimum temperature, an appropriate temperature It is necessary to maintain the refrigerant evaporation temperature of the refrigeration cycle below the difference.
If a capillary tube or a temperature-type expansion valve is used for the decompression mechanism of the refrigeration cycle as in the past, when the ambient temperature of the device is high, that is, when the refrigerant condensation temperature by the air-cooled condenser is high, the refrigerant evaporation temperature also rises and the test room minimum The temperature cannot be maintained and the temperature rises above the set minimum temperature. However, to prevent this, even when the refrigerant condensing temperature is high, if the pressure reduction amount of the capillary tube or the thermal expansion valve is determined so that the required refrigerant evaporation temperature is obtained, the ambient temperature is low, and if the refrigerant condensing temperature is low, The refrigerant evaporation temperature abnormally drops, which causes damage to the compressor due to a drop in refrigerating machine oil temperature.
Therefore, it is an important condition of this type of apparatus to maintain a refrigerant evaporation temperature that is not affected by a change in the apparatus ambient temperature, that is, a change in the refrigerant condensation temperature, and to keep the apparatus performance constant throughout the year.
【発明が解決しようとする課題】従来の恒温恒湿装置の
冷凍機制御方法にあっては、装置周囲温度の変化、すな
わち圧縮機の冷媒凝縮温度の変化に伴って冷媒蒸発温度
が変化し、年間を通して装置性能を一定に保つことがで
きない問題点があった。本発明の目的は、装置周囲温度
が変化しても冷媒蒸発温度をほぼ一定値に維持し、室内
を調温調湿することのできる恒温恒湿装置の冷凍機制御
方法及び冷凍機制御装置を提供することにある。In the conventional method of controlling a refrigerator of a constant temperature and humidity apparatus, the refrigerant evaporation temperature changes with a change in the ambient temperature of the apparatus, that is, a change in the refrigerant condensation temperature of the compressor. There was a problem that the device performance could not be kept constant throughout the year. An object of the present invention is to provide a refrigerator control method and a refrigerator control device for a constant temperature and humidity apparatus capable of maintaining a refrigerant evaporation temperature at a substantially constant value even when the ambient temperature of the apparatus changes and controlling the temperature and humidity of the room. To provide.
【課題を解決するための手段】前記の目的を達成するた
め、本発明に係る恒温恒湿装置の冷凍機制御方法は、断
熱材に囲まれた室内の温度及び湿度を測定し、それぞれ
の測定値に基づき室内に設けた加温器及び加湿器により
調温調湿制御するとともに、室内に設けた蒸発器に圧縮
機を経由して凝縮手段と減圧手段とを接続し室内を所定
温度に冷却させる冷凍機を制御する恒温恒湿装置の冷凍
機制御方法において、室内の温度及び湿度を入力して冷
凍機の冷媒状態の目標値を設定し、目標値と冷媒状態の
測定値との差に応じて圧縮機をインバータにより回転数
制御し、冷却能力を可変にする構成とする。そして断熱
材に囲まれた室内の温度及び湿度を測定し、それぞれの
測定値に基づき室内に設けた加温器及び加湿器により調
温調湿制御するとともに、室内に設けた蒸発器に圧縮機
を経由して凝縮手段と減圧手段とを接続し室内を所定温
度に冷却させる冷凍機を制御する恒温恒湿装置の冷凍機
制御方法において、冷凍機の冷媒状態に応じて冷媒状態
の目標値をあらかじめ設定し、目標値に応じて圧縮機を
インバータにより回転数制御し、冷却能力を可変にする
構成でもよい。上記の冷媒状態は、減圧手段により減圧
された冷媒のほぼ一定値に設定される冷媒蒸発温度であ
る構成でもよい。また冷媒状態は、圧縮機より吐出され
かつ凝縮手段で凝縮された冷媒の冷媒凝縮温度である構
成でもよい。 In order to achieve the above object, a method for controlling a refrigerator of a constant temperature and humidity apparatus according to the present invention measures a temperature and a humidity in a room surrounded by a heat insulating material and measures each of the measured values. Based on the value, the temperature and humidity are controlled by a heater and a humidifier provided in the room, and the condensing means and decompression means are connected to the evaporator provided in the room via a compressor to cool the room to a predetermined temperature. In the refrigerator control method of the constant temperature and humidity apparatus for controlling the refrigerator to be controlled, a target value of the refrigerant state of the refrigerator is set by inputting the indoor temperature and humidity, and a difference between the target value and the measured value of the refrigerant state is calculated. Accordingly, the compressor is controlled in rotation speed by an inverter, and the cooling capacity is made variable. The temperature and humidity in the room surrounded by the heat insulating material are measured, and the temperature and humidity are controlled by a heater and a humidifier provided in the room based on the measured values, and a compressor is provided to the evaporator provided in the room. In the refrigerating machine control method of the constant temperature and humidity apparatus for controlling the refrigerating machine that cools the room to a predetermined temperature by connecting the condensing means and the depressurizing means via the controller, the target value of the refrigerant state is set according to the refrigerant state of the refrigerating machine. The compressor may be set in advance and the number of revolutions of the compressor may be controlled by an inverter according to a target value to vary the cooling capacity . The refrigerant state may be a refrigerant evaporation temperature set to a substantially constant value of the refrigerant depressurized by the decompression means . Further, the refrigerant state may be a refrigerant condensing temperature of the refrigerant discharged from the compressor and condensed by the condensing means .
【作用】本発明によれば、回転式圧縮機の電源周波数を
変化させると、◆ 回転数（ｒ．ｐ．ｍ）＝（１２０／ｐ）×ｆ◆ ｐ＝極数， ｆ＝周波数◆ で示されるように、周波数に比例して回転式圧縮機の回
転数が変化する。回転数が変化すると冷媒の吐出量が変
化して冷媒循環量が変化し、冷却能力が変化する。例え
ば装置周囲温度が高く、冷凍機の冷媒凝縮温度が高い場
合、冷媒蒸発温度も高くなるが、周波数を高くして回転
式圧縮機の回転数を上昇させると、冷媒循環量が増加し
て冷媒凝縮温度が低下し、所定の冷却能力が得られる。
電源周波数は制御手段に入力される室内の測定温度によ
り決定される目標冷媒蒸発温度に対して、測定冷媒蒸発
温度を比較演算し、目標冷媒蒸発温度と測定冷媒蒸発温
度とを近似させることにより、最適な冷却能力が供給さ
れて装置周囲温度の変化による冷媒凝縮温度の変化に伴
う冷却能力の変化が抑制され、装置性能が年間を通して
一定に保たれる。According to the present invention, when the power supply frequency of the rotary compressor is changed, {rotational speed (rpm) = (120 / p) × f} p = pole number, f = frequency As shown, the rotational speed of the rotary compressor changes in proportion to the frequency. When the rotation speed changes, the discharge amount of the refrigerant changes, the refrigerant circulation amount changes, and the cooling capacity changes. For example, when the ambient temperature of the device is high and the refrigerant condensing temperature of the refrigerator is high, the refrigerant evaporation temperature is also high.However, when the frequency is increased and the rotation speed of the rotary compressor is increased, the refrigerant circulation amount increases and the refrigerant circulates. The condensing temperature decreases, and a predetermined cooling capacity is obtained.
The power supply frequency is calculated by comparing the measured refrigerant evaporation temperature with the target refrigerant evaporation temperature determined by the indoor measured temperature input to the control means, and approximating the target refrigerant evaporation temperature and the measured refrigerant evaporation temperature. An optimum cooling capacity is supplied, and a change in the cooling capacity due to a change in the refrigerant condensing temperature due to a change in the apparatus ambient temperature is suppressed, and the apparatus performance is kept constant throughout the year.
【実施例】本発明の第１の実施例を図１を参照しながら
説明する。図１に示すように、恒温恒湿装置は断熱層１
により囲まれた試験室（室）２と、冷媒１４を循環する
周波数制御可能な回転式圧縮機９と、回転式圧縮機９よ
り吐出した冷媒ガスを冷媒液に空気冷却する凝縮器１０
と凝縮器１０に送風する凝縮器用送風機１１とよりなる
凝縮手段と、冷媒１４を減圧する減圧機構（減圧手段）
１２と、試験室２内に設けられ減圧された冷媒１４で試
験室２内の熱を吸収する蒸発器１３と、試験室２内を加
温制御する加温ヒータ７と、試験室内を加湿制御する加
湿ヒータ８と、試験室２内の循環送風機５と、図示しな
い制御手段とにより構成される。試験室２内を空気の流
れ６が矢印図示のように循環している。循環送風機５の
吹出口には乾球温度センサ３及び湿球温度センサ４が配
置され、さらに減圧機構１２の冷媒出口側で、蒸発器１
３までの配管系路に冷媒蒸発温度センサ１５を取付けて
ある。なお圧縮機は定速のものを搭載し、減圧機構を電
子膨張弁で形成した構成でもよい。本装置の制御系路
（制御手段）を図２を参照しながら説明する。乾球温度
センサ３及び湿球温度センサ４の各々の検出温度は、室
内の設定温度及び設定湿度との比較演算をマイクロコン
ピュータ２０で行ない、ヒータ出力制御器２１，２２で
加温ヒータ７及び加湿ヒータ８への出力信号をＰＩＤ制
御することにより、高精度の調温調湿制御を可能として
いる。これに対し、除湿冷却用として用いられる冷凍サ
イクルは、乾球温度センサ３及び湿球温度センサ４の各
々の検出温度に基づき冷媒状態の目標値の設定と冷媒状
態の測定値との差、例えば冷媒蒸発温度センサ１５によ
る検出温度と設定冷媒蒸発温度との差の比較演算をマイ
コン２０で行い、周波数制御器２３で回転式圧縮機の回
転数を制御するための周波数をＰＩＤ制御している。な
お冷媒状態は、圧縮機に吸入される冷媒の低圧圧力、圧
縮機より吐出されかつ凝縮手段で凝縮された冷媒の冷媒
凝縮温度、又は圧縮機より吐出された冷媒の高圧圧力の
いずれでもよく、また設定冷媒蒸発温度等の目標値は室
内の温度及び湿度に応じて装置の仕様上あらかじめ決め
られていてもよい。さらに減圧手段を電子膨張弁で形成
して圧縮機は定速のものを搭載し、電子膨張弁をマイコ
ンにより開度制御するようにしてもよい。回転式圧縮機
の周波数制御のフローチャートを図３に示す。回転式圧
縮機は電源周波数の変化に応じて回転数が変化し、冷媒
循環量が増減するものであり、回転式圧縮機の運転開始
と同時に初期設定周波数で回転し、これ以降は、常時、
蒸発温度センサの測定温度と目標冷媒蒸発温度との差の
比較演算を行い、測定温度が高い場合は周波数増とし、
また低い場合は周波数減とし、さらに増減量はＰＩＤ制
御することにより回転式圧縮機へ伝送する最適な電源周
波数を決定し、測定冷媒蒸発温度を目標冷媒蒸発温度に
近似させ、さらに一致させる運転が可能となる。本発明
の第２の実施例を図４を参照しながら説明する。第１の
実施例における冷媒蒸発温度センサのかわりに、冷凍サ
イクル低圧力センサを用いた構成である。減圧機構１２
と蒸発器１３とを介して回転式圧縮機９との間に低圧圧
力センサ１６を取付けることにより、第１の実施例にお
ける設定冷媒蒸発温度と検出温度との比較演算と同様
に、目標低圧圧力と検出圧力との比較演算を行い回転式
圧縮機の周波数を制御し、目標低圧圧力と検出圧力とを
近似させることが可能となる。本発明の第３の実施例を
図５を参照しながら説明する。第１の実施例における冷
媒蒸発温度センサのかわりに、冷凍サイクル凝縮温度セ
ンサを用いた構成である。凝縮器１０の内部又は凝縮器
１０の出口部に冷媒凝縮温度センサ１７を取付けること
により、冷媒凝縮温度を検出し、あらかじめ冷媒凝縮温
度に対し冷媒蒸発温度を一定に保つために必要な回転式
圧縮機の周波数を設定しておく。この制御例を図６に示
す。第３の実施例により、装置周囲温度の変化に伴う冷
媒凝縮温度の変化に応じた設定周波数で、回転式圧縮機
を運転することにより冷媒蒸発温度を一定に保つことが
可能となる。本発明の第４の実施例を図７を参照しなが
ら説明する。第３の実施例における冷媒凝縮温度センサ
のかわりに、冷凍サイクル高圧圧力センサを用いた構成
である。回転式圧縮機９と減圧機構１２との間に高圧圧
力センサ１８を取付けることにより冷媒の高圧圧力を検
出し、第３の実施例における検出した冷媒凝縮温度によ
る回転式圧縮機の周波数設定のかわりに、検出した高圧
圧力により周波数を設定することにより同一の効果を得
ることができる。本発明の第５の実施例を図８を参照し
ながら説明する。第３の実施例における冷媒凝縮温度セ
ンサのかわりに空気温度センサを用いた場合を図８に示
す。装置周辺部又は凝縮器１０の空気吸込部に空気温度
センサ１９を取付けることにより、空気温度（装置周囲
温度）を検出し第３の実施例における検出した冷媒凝縮
温度による回転式圧縮機の周波数設定のかわりに、検出
した空気温度により周波数を設定することにより同一の
効果を得ることができる。本発明により、装置周囲温度
の変化、すなわち冷媒凝縮温度の変化に対して、冷媒蒸
発温度を目標温度に維持し、安定させることができる。
本発明による回転式圧縮機の周波数制御と冷凍サイクル
特性の一例を図９に示す。本発明の冷媒蒸発温度による
周波数制御を採用することにより、装置周囲温度が変化
し、冷媒凝縮温度が変化しても、冷媒蒸発温度は設定冷
媒蒸発温度である−４５℃を一定に保つことができ、こ
の結果、試験室設定温度−４０℃を年間を通して維持
し、安定を保つことが可能となる。なお、従来技術によ
る周波数固定（６０Ｈｚ）の場合は、図９中に破線で示
すように、装置周囲温度変化に対し、冷媒蒸発温度が変
化し、この結果、周囲高温時試験室温度が−４０℃を維
持することができなくなる。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG. As shown in FIG. 1, the thermo-hygrostat is a heat insulating layer 1
(Chamber) 2 surrounded by a circle, a frequency-controllable rotary compressor 9 circulating a refrigerant 14, and a condenser 10 for air-cooling a refrigerant gas discharged from the rotary compressor 9 to a refrigerant liquid.
And a condenser blower 11 for blowing air to the condenser 10, and a decompression mechanism (decompression means) for decompressing the refrigerant 14.
12, an evaporator 13 provided in the test chamber 2 for absorbing the heat in the test chamber 2 by the depressurized refrigerant 14, a heating heater 7 for heating and controlling the inside of the test chamber 2, and a humidification control for the test chamber. A humidifying heater 8, a circulating blower 5 in the test chamber 2, and control means (not shown). An air flow 6 circulates in the test chamber 2 as shown by the arrow. A dry-bulb temperature sensor 3 and a wet-bulb temperature sensor 4 are disposed at the outlet of the circulating blower 5.
Refrigerant evaporation temperature sensors 15 are mounted on up to three piping systems. The compressor may have a constant speed, and the pressure reducing mechanism may be formed by an electronic expansion valve. The control system (control means) of the present apparatus will be described with reference to FIG. The microcomputer 20 compares the detected temperatures of the dry-bulb temperature sensor 3 and the wet-bulb temperature sensor 4 with the indoor set temperature and the set humidity, and the heater output controllers 21 and 22 heat the heater 7 and the humidifier. By controlling the output signal to the heater 8 by PID control, highly accurate temperature and humidity control can be performed. On the other hand, the refrigeration cycle used for dehumidifying cooling is based on the detected temperature of each of the dry-bulb temperature sensor 3 and the wet-bulb temperature sensor 4, and the difference between the setting of the target value of the refrigerant state and the measured value of the refrigerant state, for example, The microcomputer 20 performs a comparison operation of the difference between the detected temperature of the refrigerant evaporation temperature sensor 15 and the set refrigerant evaporation temperature, and the frequency controller 23 performs PID control of the frequency for controlling the rotation speed of the rotary compressor. The refrigerant state may be any one of the low pressure of the refrigerant sucked into the compressor, the refrigerant condensation temperature of the refrigerant discharged from the compressor and condensed by the condensing means, or the high pressure of the refrigerant discharged from the compressor, Further, the target values such as the set refrigerant evaporation temperature may be determined in advance in the specifications of the apparatus in accordance with the indoor temperature and humidity. Further, the pressure reducing means may be formed by an electronic expansion valve, a compressor of a constant speed may be mounted, and the opening of the electronic expansion valve may be controlled by a microcomputer. FIG. 3 shows a flowchart of frequency control of the rotary compressor. The rotary compressor changes its rotation speed in accordance with a change in the power supply frequency, and the amount of circulating refrigerant increases and decreases.The rotary compressor rotates at an initial set frequency simultaneously with the start of operation of the rotary compressor.
Perform a comparison operation of the difference between the measured temperature of the evaporation temperature sensor and the target refrigerant evaporation temperature, and if the measured temperature is high, increase the frequency,
When the frequency is low, the frequency is decreased, and the amount of increase or decrease is determined by PID control to determine an optimum power supply frequency to be transmitted to the rotary compressor, and the measured refrigerant evaporation temperature is approximated to the target refrigerant evaporation temperature. It becomes possible. A second embodiment of the present invention will be described with reference to FIG. This is a configuration using a refrigeration cycle low pressure sensor instead of the refrigerant evaporation temperature sensor in the first embodiment. Decompression mechanism 12
By attaching the low pressure sensor 16 between the rotary compressor 9 and the rotary compressor 9 via the evaporator 13, the target low pressure pressure is set in the same manner as in the comparison calculation between the set refrigerant evaporation temperature and the detected temperature in the first embodiment. And the detected pressure is compared to control the frequency of the rotary compressor so that the target low pressure and the detected pressure can be approximated. A third embodiment of the present invention will be described with reference to FIG. This is a configuration using a refrigeration cycle condensation temperature sensor instead of the refrigerant evaporation temperature sensor in the first embodiment. By installing the refrigerant condensation temperature sensor 17 inside the condenser 10 or at the outlet of the condenser 10, the refrigerant condensation temperature is detected, and the rotary compression required for keeping the refrigerant evaporation temperature constant with respect to the refrigerant condensation temperature in advance. Set the machine frequency. FIG. 6 shows an example of this control. According to the third embodiment, it is possible to keep the refrigerant evaporation temperature constant by operating the rotary compressor at a set frequency according to the change in the refrigerant condensation temperature accompanying the change in the device ambient temperature. A fourth embodiment of the present invention will be described with reference to FIG. This is a configuration using a refrigeration cycle high-pressure sensor instead of the refrigerant condensation temperature sensor in the third embodiment. A high pressure sensor 18 is mounted between the rotary compressor 9 and the pressure reducing mechanism 12 to detect the high pressure of the refrigerant. Instead of setting the frequency of the rotary compressor based on the detected refrigerant condensation temperature in the third embodiment. By setting the frequency based on the detected high pressure, the same effect can be obtained. A fifth embodiment of the present invention will be described with reference to FIG. FIG. 8 shows a case where an air temperature sensor is used instead of the refrigerant condensation temperature sensor in the third embodiment. By attaching an air temperature sensor 19 to the peripheral portion of the device or to the air suction portion of the condenser 10, the air temperature (device ambient temperature) is detected, and the frequency of the rotary compressor is set based on the detected refrigerant condensation temperature in the third embodiment. Instead, the same effect can be obtained by setting the frequency based on the detected air temperature. According to the present invention, it is possible to maintain and stabilize the refrigerant evaporation temperature at the target temperature with respect to a change in the device ambient temperature, that is, a change in the refrigerant condensation temperature.
FIG. 9 shows an example of frequency control and refrigeration cycle characteristics of the rotary compressor according to the present invention. By employing the frequency control based on the refrigerant evaporation temperature of the present invention, even if the ambient temperature of the apparatus changes and the refrigerant condensation temperature changes, the refrigerant evaporation temperature can keep the set refrigerant evaporation temperature of -45 ° C constant. As a result, the test room set temperature of −40 ° C. can be maintained throughout the year, and the stability can be maintained. In the case of the fixed frequency (60 Hz) according to the prior art, as shown by the broken line in FIG. 9, the refrigerant evaporation temperature changes with respect to the change in the device ambient temperature. C cannot be maintained.
【発明の効果】本発明によれば、装置周囲温度の変化、
すなわち冷媒凝縮温度の変化に対して、冷媒蒸発温度を
目標温度に維持し、安定させることができるため、室内
の設定温度が年間を通して高精度に維持され、安定化す
ることが可能となる。According to the present invention, a change in the ambient temperature of the device,
That is, the refrigerant evaporation temperature can be maintained at the target temperature and stabilized with respect to the change in the refrigerant condensing temperature, so that the indoor set temperature can be maintained and stabilized with high accuracy throughout the year.
【図１】本発明の第１の実施例を示す構成図である。FIG. 1 is a configuration diagram showing a first embodiment of the present invention.
【図２】図１の制御系路を示すフローチャートである。FIG. 2 is a flowchart showing a control system of FIG. 1;
【図３】図１の回転式圧縮機の周波数制御を示すフロー
チャートである。FIG. 3 is a flowchart illustrating frequency control of the rotary compressor of FIG. 1;
【図４】本発明の第２の実施例を示す構成図である。FIG. 4 is a configuration diagram showing a second embodiment of the present invention.
【図５】本発明の第３の実施例を示す構成図である。FIG. 5 is a configuration diagram showing a third embodiment of the present invention.
【図６】本発明実施例３による冷媒凝縮温度と設定圧縮
機周波数FIG. 6 shows a refrigerant condensing temperature and a set compressor frequency according to Embodiment 3 of the present invention.
【図７】本発明の第４の実施例を示す構成図である。FIG. 7 is a configuration diagram showing a fourth embodiment of the present invention.
【図８】本発明の第５の実施例を示す構成図である。FIG. 8 is a configuration diagram showing a fifth embodiment of the present invention.
【図９】本発明による圧縮機周波数制御と冷凍サイクル
特性とを示す図である。FIG. 9 is a diagram showing compressor frequency control and refrigeration cycle characteristics according to the present invention.
３ 乾球温度センサ ４ 湿球温度センサ ７ 加温ヒータ ８ 加湿ヒータ ９ 回転式圧縮機 １０ 凝縮器 １２ 電子式比例制御弁 １３ 蒸発器 １４ 冷媒 １５ 冷媒蒸発温度センサ １６ 低圧圧力センサ １７ 冷媒凝縮温度センサ １８ 高圧圧力センサ １９ 空気温度センサ Reference Signs List 3 Dry bulb temperature sensor 4 Wet bulb temperature sensor 7 Heating heater 8 Humidifying heater 9 Rotary compressor 10 Condenser 12 Electronic proportional control valve 13 Evaporator 14 Refrigerant 15 Refrigerant evaporation temperature sensor 16 Low pressure pressure sensor 17 Refrigerant condensation temperature sensor 18 High pressure sensor 19 Air temperature sensor
───────────────────────────────────────────────────── フロントページの続き (72)発明者 尾川 健男 静岡県清水市村松390番地 株式会社 日立製作所 清水工場内 (72)発明者 櫻野 正敏 静岡県清水市村松390番地 株式会社 日立製作所 清水工場内 (56)参考文献 特開 平５−96185（ＪＰ，Ａ) 特開 昭64−63774（ＪＰ，Ａ) 特開 平１−147259（ＪＰ，Ａ) (58)調査した分野(Int.Cl.7，ＤＢ名) F25B 1/00 F24F 11/02 102 B01L 7/00 B01L 11/02 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Takeo Ogawa 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture Inside the Shimizu Plant, Hitachi, Ltd. (56) reference Patent flat 5-96185 (JP, a) JP Akira 64-63774 (JP, a) JP flat 1-147259 (JP, a) (58 ) investigated the field (Int.Cl. 7 , DB name) F25B 1/00 F24F 11/02 102 B01L 7/00 B01L 11/02
Claims (2)
測定し、それぞれの測定値に基づき前記室内に設けた加
温器及び加湿器により調温調湿制御するとともに、前記
室内に設けた蒸発器に圧縮機を経由して凝縮手段と減圧
手段とを接続してなる冷凍機により前記室内を所定温度
に冷却させるよう制御する恒温恒湿装置の冷凍制御方法
において、前記室内に対して室外に前記減圧手段の冷媒
出口側で前記蒸発器までの配管経路に取り付けられた冷
媒蒸発温度センサを備え、前記室内の温度及び湿度を入
力して前記冷凍機の冷媒蒸発温度の目標値を設定し、該
目標値と前記冷媒蒸発温度センサの測定値との差に応じ
て前記圧縮機をインバータにより回転数制御し、冷却能
力を可変にすることを特徴とする恒温恒湿装置の冷凍制
御方法。A temperature and humidity in a room surrounded by a heat insulating material are measured, and a temperature and humidity are controlled by a heater and a humidifier provided in the room based on respective measured values, and provided in the room. the refrigerating method of controlling a constant temperature and humidity device for controlling so as to cool the chamber to a predetermined temperature by the evaporator via the compressor becomes connected to the condensing means and decompression means refrigerator was, relative to the chamber The refrigerant of the decompression means outside the room
A cooling system attached at the outlet side to the piping route to the evaporator
A medium evaporation temperature sensor, inputting the indoor temperature and humidity to set a target value of the refrigerant evaporation temperature of the refrigerator , and according to a difference between the target value and a measurement value of the refrigerant evaporation temperature sensor, A refrigeration control method for a constant-temperature and constant-humidity device, wherein a rotation speed of a compressor is controlled by an inverter to make a cooling capacity variable.
測定し、それぞれの測定値に基づき前記室内に設けた加
温器及び加湿器により調温調湿制御するとともに、前記
室内に設けた蒸発器に圧縮機を経由して凝縮手段と減圧
手段とを接続してなる冷凍機により前記室内を所定温度
に冷却させるよう制御する恒温恒湿装置の冷凍制御方法
において、前記室内に対して室外に前記凝縮手段の出口
部に取り付けられた冷媒凝縮温度センサを備え、前記室
内の温度及び湿度を入力して前記冷凍機の冷媒凝縮温度
の目標値を設定し、該目標値と前記冷媒凝縮温度センサ
の測定値との差に応じて前記圧縮機をインバータにより
回転数制御し、冷却能力を可変にすることを特徴とする
恒温恒湿装置の冷凍制御方法。2. The temperature and humidity of a room surrounded by a heat insulating material are measured, and the temperature and humidity are controlled by a heater and a humidifier provided in the room based on the respective measured values, and the temperature and humidity are provided in the room. the refrigerating method of controlling a constant temperature and humidity device for controlling so as to cool the chamber to a predetermined temperature by the evaporator via the compressor becomes connected to the condensing means and decompression means refrigerator was, relative to the chamber Outlet of the condensation means outside the room
A refrigerant condensing temperature sensor attached to the section,
Enter the temperature and humidity inside the refrigerator and the refrigerant condensation temperature of the refrigerator
The target value and the refrigerant condensing temperature sensor
A method for controlling the refrigerating of a thermo-hygrostat, characterized in that the compressor is controlled in rotation speed by an inverter according to the difference between the measured value and the cooling capacity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5137637A JP3023637B2 (en) | 1993-06-08 | 1993-06-08 | Refrigeration control method for constant temperature and humidity apparatus |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP5137637A JP3023637B2 (en) | 1993-06-08 | 1993-06-08 | Refrigeration control method for constant temperature and humidity apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06347107A JPH06347107A (en) | 1994-12-20 |
| JP3023637B2 true JP3023637B2 (en) | 2000-03-21 |
Family
ID=15203300
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP5137637A Expired - Fee Related JP3023637B2 (en) | 1993-06-08 | 1993-06-08 | Refrigeration control method for constant temperature and humidity apparatus |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3023637B2 (en) |
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