JPH0359351A - Air conditioner - Google Patents
Air conditionerInfo
- Publication number
- JPH0359351A JPH0359351A JP19325489A JP19325489A JPH0359351A JP H0359351 A JPH0359351 A JP H0359351A JP 19325489 A JP19325489 A JP 19325489A JP 19325489 A JP19325489 A JP 19325489A JP H0359351 A JPH0359351 A JP H0359351A
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- Prior art keywords
- temperature
- compressor
- pressure
- detected
- discharge
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- Air Conditioning Control Device (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野Ｊ
この発明は、空気調和機の改良に関するものであり、特
に、空気調和機に使用される圧ａ機を良好な状態で運転
継続させる制御に関するものである。DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application J This invention relates to improvement of air conditioners, and particularly relates to control for continuing operation of a pressure-a machine used in an air conditioner in good condition. It is something.
従来、この程の空気調和機として第３図に示すものがあ
る。図中、（１）は回転数を切換えることにより圧縮容
量が調整可能な圧縮機、（２）は四方弁、（３）は室外
熱交換器、（４）は減圧装置、（５）は室内熱交換器、
（６）はアキュムレータ、（７）は圧力検出手段である
。尚、図中、実線矢印は冷房運転時の冷媒流れ方向、破
線矢印は暖房運転時の冷媒流れ方向を示す。A conventional air conditioner of this type is shown in FIG. In the figure, (1) is a compressor whose compression capacity can be adjusted by changing the rotation speed, (2) is a four-way valve, (3) is an outdoor heat exchanger, (4) is a pressure reducing device, and (5) is an indoor Heat exchanger,
(6) is an accumulator, and (7) is a pressure detection means. In addition, in the figure, solid line arrows indicate the refrigerant flow direction during cooling operation, and broken line arrows indicate the refrigerant flow direction during heating operation.
次に、冷房運転時の動作について説明する。圧縮機（１
）で圧縮された冷媒ガスは、四方弁（２）を介して室外
熱交換器（３）に流入し、室外空気に放熱する一方、冷
媒は凝縮して高圧の液冷媒となり、減圧装置（４）で減
圧され低圧の気液混合冷媒となり、室内熱交換器（５）
に流入し、室内空気よシ採熱して冷房運転する一方、冷
媒は低圧のガス冷媒となり、四方弁（２）を介してアキ
ュムレータ（６）に流入する。Next, the operation during cooling operation will be explained. Compressor (1
) The refrigerant gas compressed by the four-way valve (2) flows into the outdoor heat exchanger (3) and radiates heat to the outdoor air, while the refrigerant condenses to become a high-pressure liquid refrigerant and is transferred to the pressure reducing device (4). ) to become a low-pressure gas-liquid mixed refrigerant, which is then transferred to the indoor heat exchanger (5).
The refrigerant flows into the accumulator (6) via the four-way valve (2) as a low-pressure gas refrigerant while collecting heat from the indoor air and performing cooling operation.
アキュムレータ（６）では、室内熱交換器（５）で蒸発
し切れなかった液冷媒とが又冷媒を分離して、ガス冷媒
のみを圧縮機（１）に吸入させる。また、圧縮機（１）
は圧力検出手段（７）で検出される低圧側の圧力値が所
定範囲内に入るように回転数が制御される。In the accumulator (6), the refrigerant is separated from the liquid refrigerant that has not been completely evaporated in the indoor heat exchanger (5), and only the gas refrigerant is sucked into the compressor (1). Also, compressor (1)
The rotation speed is controlled so that the pressure value on the low pressure side detected by the pressure detection means (7) falls within a predetermined range.
また、暖房運転時には、圧縮機（１）にて圧縮された高
温高圧のガス冷媒は、四方弁伐）を介して室内熱交換器
（５）に流入し、室内空気に対して放熱して暖房運転す
る一方、冷媒は凝縮して高圧の液冷媒となり、減圧装置
（４）で減圧され低圧の気液混合冷媒となう、室外熱交
換器（３）に流入し、室外空気より採熱する一方、冷媒
は低圧のガス冷媒となり、四方弁（２）およびアキュム
レータ（６）を介して圧縮機（１）に吸入される。尚、
暖房運転時には、圧力検出手段（７）での検知圧力は高
圧圧力となう、高圧圧力が所定範囲内に入るように、圧
縮機（１）の回転数が制御される。In addition, during heating operation, the high-temperature, high-pressure gas refrigerant compressed by the compressor (1) flows into the indoor heat exchanger (5) via the four-way valve, radiates heat to the indoor air, and heats the room. During operation, the refrigerant condenses to become a high-pressure liquid refrigerant, which is depressurized by the pressure reducing device (4) and becomes a low-pressure gas-liquid mixed refrigerant.The refrigerant flows into the outdoor heat exchanger (3) and collects heat from the outdoor air. On the other hand, the refrigerant becomes a low-pressure gas refrigerant and is sucked into the compressor (1) via the four-way valve (2) and the accumulator (6). still,
During the heating operation, the rotation speed of the compressor (1) is controlled so that the pressure detected by the pressure detection means (7) is a high pressure, and the high pressure falls within a predetermined range.
従来の空気調和機は、以上の如く構成されていたので、
圧縮機（１）起動前に、圧縮機（１）内部あるいはアキ
ュムレータ（６）内に液冷媒が寝込んでいた場合には、
起動直後に圧縮機（１）に冷媒液が流入し、いわゆる液
バツクを伴い、吐出弁の損傷とか、冷凍機油が液冷媒で
希釈され、摺動部の焼付事故を伴うという問題が発生す
る。更に、圧縮機（１）の運転周波数を前述の如き液バ
ツク状態で上昇させた場合には、摺動部の軸受負荷も増
大するために、軸受の事故が多発する可能性が高くなる
。Conventional air conditioners were configured as described above,
If liquid refrigerant is trapped inside the compressor (1) or the accumulator (6) before starting the compressor (1),
Immediately after startup, refrigerant liquid flows into the compressor (1), resulting in a so-called liquid backlash, which causes problems such as damage to the discharge valve and dilution of the refrigerating machine oil with the liquid refrigerant, resulting in seizure of sliding parts. Furthermore, if the operating frequency of the compressor (1) is increased in the liquid back-up condition as described above, the bearing load on the sliding parts will also increase, increasing the possibility that bearing accidents will occur frequently.
この発明は、前述の如き問題点を解決するためになされ
たものであり、圧縮機（１）の起動直後並びに運転中に
一時的に液バツクが発生した場合でも、圧縮機（１）の
運転状態を良好に保つことを目的としている。This invention was made in order to solve the above-mentioned problems, and even if liquid back-up occurs temporarily immediately after the compressor (1) is started or during operation, the compressor (1) can be operated. The purpose is to keep it in good condition.
〔課題を解決するための手段Ｊ
この発明に係わる空気調和機は、圧縮機吐出温度を検出
する吐出温度検出手段と、吐出圧力を検出する吐出圧力
検出手段と、前記吐出圧力検出手段による検出圧力に相
当する冷媒飽和温度を換算する飽和温度換算手段、及び
前記吐出温度検出手段による検出温度と前記飽和温度換
算手段による飽和温度とを比較し、その差温を検出する
温度比較手段とを備え、前記温度比較手段による差温か
所定値以下の場合には、圧縮機の圧縮容量を増加させな
いようにしたものである。[Means for Solving the Problems J] An air conditioner according to the present invention includes a discharge temperature detection means for detecting a compressor discharge temperature, a discharge pressure detection means for detecting a discharge pressure, and a pressure detected by the discharge pressure detection means. a saturation temperature conversion means for converting a refrigerant saturation temperature corresponding to , and a temperature comparison means for comparing the temperature detected by the discharge temperature detection means and the saturation temperature by the saturation temperature conversion means and detecting a temperature difference therebetween, The compression capacity of the compressor is not increased when the temperature difference determined by the temperature comparison means is less than a predetermined value.
また、前述の吐出温度による圧縮容量の増加禁止制御は
圧縮機起動後の所定時間は無効化するようにしたもので
ある。Further, the above-mentioned control for inhibiting the increase in compression capacity based on the discharge temperature is disabled for a predetermined period of time after the compressor is started.
［作用］
この空気調和機では、圧縮機の圧縮容量増加を吐出温度
で抑制するようにしたので、液バツク運転時に圧縮機の
軸受負荷が増大する運転容量の増加を禁止することにな
る。[Function] In this air conditioner, an increase in the compression capacity of the compressor is suppressed by the discharge temperature, so an increase in the operating capacity that would increase the bearing load of the compressor during liquid back operation is prohibited.
更に圧縮機起動直後で吐出温度がｆ分上昇しない所定時
間は圧縮機容量の増加禁止制御を無効化することによう
、誤動作による圧縮容量の増加が遅れることもない。Furthermore, since the compressor capacity increase prohibition control is disabled for a predetermined period of time when the discharge temperature does not rise by f minutes immediately after the compressor is started, there is no delay in increasing the compression capacity due to malfunction.
以下、この発明の一実施例を第１図に基づき説明する。 An embodiment of the present invention will be described below with reference to FIG.
図中、（１）〜（６）は第３図に示す従来の空気調和機
のものと同一であり、（８）は圧縮機（１）の吐出圧力
を検出する吐出圧力検出手段、（９）は圧縮機（１）の
吐出温度を検出する吐出温度検出手段、（１１）は室外
熱交換器（３）と減圧装置（４）を接続する配管途中よ
う毛細管（１０）を介して四方弁伐）とアキュムレータ
（６）を接続する配管に至る蒸発温度生成回路であり、
（１２）は前記蒸発温度生成回路（１１）を流れる冷媒
温度を検出する蒸発温度検出装置、（１３）は圧縮機（
１）の運転容量を制御する運転容量制御手段、（１４）
は吐出圧力検出手段（８）の検出圧力に基づき、検出圧
力に相当する飽和温度を換算する飽和温度換算手段、（
１５）は前記飽和温度換算手段による換算温度と前記吐
出温度検出手段（９）により検出される検出温度を比較
する温度比較手段である。尚、図中実線矢印は冷房運転
時の冷媒流れ方向を示し破線矢印は暖房運転時の冷媒流
れ方向を示す。In the figure, (1) to (6) are the same as those of the conventional air conditioner shown in FIG. 3, (8) is a discharge pressure detection means for detecting the discharge pressure of the compressor (1), (9) ) is a discharge temperature detection means for detecting the discharge temperature of the compressor (1), and (11) is a four-way valve that connects the outdoor heat exchanger (3) and the pressure reduction device (4) through a capillary tube (10) in the piping. This is an evaporation temperature generation circuit leading to the piping that connects the (6) and the accumulator (6).
(12) is an evaporation temperature detection device that detects the temperature of the refrigerant flowing through the evaporation temperature generation circuit (11); (13) is a compressor (
(14) operating capacity control means for controlling the operating capacity of 1);
is a saturation temperature conversion means for converting a saturation temperature corresponding to the detected pressure based on the detected pressure of the discharge pressure detection means (8);
15) is a temperature comparing means for comparing the converted temperature by the saturation temperature converting means and the detected temperature detected by the discharge temperature detecting means (9). In addition, the solid line arrow in the figure indicates the refrigerant flow direction during cooling operation, and the broken line arrow indicates the refrigerant flow direction during heating operation.
冷房運転時並びに暖房運転時の冷媒側の基本的な動作は
、第３図に示す従来の空気調和機と同様であるので説明
を省略する。但し、蒸発温度生成回路（１１）では、冷
房運転時に室外熱交換器（３）にて凝縮した高圧の冷媒
液の一部が、毛細管（１０）を介してアキュムレータ（
６）の流入配管に流れるため、蒸発温度検出装置（１２
）の取付部では低圧の気液混合冷媒となっており、低圧
圧力の相当飽和温度を正確に検知することができる。ま
た、運転容量制御手段（１３）は冷房運転時には前記蒸
発温度検出装置（１２）による検出温度が一定範囲内に
入るように圧縮機（１）の運転容量を制御すると共に、
暖房運転時には、吐出圧力検出手段（８）による検出圧
力が一定範囲内に入るように圧縮機（１）の運転容量を
制御するものである。また、飽和温度換算手段（１４）
では、吐出圧力検出手段（８）の検出圧力と冷媒回路に
使用している冷媒特性に基づき、冷媒の飽和温度を１次
あるいは２次式で近似させるものである。The basic operation on the refrigerant side during cooling operation and heating operation is the same as that of the conventional air conditioner shown in FIG. 3, so a description thereof will be omitted. However, in the evaporation temperature generation circuit (11), a part of the high-pressure refrigerant liquid condensed in the outdoor heat exchanger (3) during cooling operation flows through the capillary tube (10) to the accumulator (
6), so the evaporation temperature detection device (12
) is a low-pressure gas-liquid mixed refrigerant at the attachment point, and the equivalent saturation temperature of the low pressure can be accurately detected. Further, the operating capacity control means (13) controls the operating capacity of the compressor (1) so that the temperature detected by the evaporation temperature detection device (12) falls within a certain range during cooling operation, and
During heating operation, the operating capacity of the compressor (1) is controlled so that the pressure detected by the discharge pressure detection means (8) falls within a certain range. Also, saturation temperature conversion means (14)
Here, the saturation temperature of the refrigerant is approximated by a linear or quadratic equation based on the pressure detected by the discharge pressure detection means (8) and the characteristics of the refrigerant used in the refrigerant circuit.
更に、温度比較手段（１５）では前記飽和温度換算手段
（１４）で得られた飽和温度と吐出温度検出手段（９）
により検出される吐出温度とを比較し、上記吐出温度と
上記飽和温度との差温が所定値以上の場合には、圧縮機
（１）の運転が良好であり、所定値未満の場合には、圧
縮機（１）は液パツク状態で運転していると判定し、運
転容量制御手段（１３）に対し補正を加えるものである
。Furthermore, the temperature comparison means (15) calculates the saturation temperature obtained by the saturation temperature conversion means (14) and the discharge temperature detection means (9).
Compare the discharge temperature detected by , it is determined that the compressor (1) is operating in a liquid pack state, and a correction is made to the operating capacity control means (13).
以下、第２図に示すフローチャートに基づき、暖房運転
時にかける、運転容量制御手段（１３）＞よび温度比較
手段（１５）の動作について説明する。筐ず、ステップ
（２０）で暖房運転が開始されると、予め設定された周
波数でステップ（２１）で圧縮機（１）は起動し、ステ
ップ（２２）で圧縮機（１）の起動後所定時間（例えば
３分間）が経過したか否かを判定し、所定時間未満の場
合には、ステップ（２５）に進み吐出圧力検出装置（８
）による検出圧力Ｐｄが制御圧力Ｐｃに対し差圧１砂智
の範囲内に入っているか否かを判定し、制御圧力範囲内
に入っている場合にはステップ（２７）に進み周波数を
維持する。また、ステップ（２５）の判定で、検出圧力
Ｐｄが制御圧力Ｐｃに対してＩＫ／ｃＩｊ以上低い場合
にはステップ（２６）に進んで周波数を所定値だけ増加
し、検出圧力Ｐｄが制御圧力Ｐｃに対してＩ Ｋｇｌｃ
ｄ以上高い場合にはステップ（２８）に進んで周波数を
所定値だけ減少し、このような動作を繰シ返すことによ
り最終的に検出圧力Ｐｄが制御圧力Ｐｃに対して一定範
囲内に入るように、圧縮機（１）の運転容量が制御され
る。尚、ステップ（２２）で圧縮機（１）の起動後所定
時間経過した場合には、ステップ（２３）に進んで、検
出圧力Ｐｄに基づき飽和温度換算手段（１４）により飽
和温度Ｔｃを求め、ステップ（２４）に進み、吐出温度
検出手段（９）による検出温度Ｔｄと飽和温度Ｔｃを比
較し、ＴｄがＴｃに対して１５ｄｅｇ以上高ければステ
ップ（２５）に進み通常の圧力に基づく周波数制御ル−
チンに進む。また、ステップ（２４）にかいて、検出温
度Ｔｄが飽和温度Ｔｃに対して１５ｄｅ＜以上の差温か
ない場合には、ステップ（２７）に進んで周波数を維持
し、運転容量の増加を禁止する。Hereinafter, based on the flowchart shown in FIG. 2, the operations of the operating capacity control means (13) and the temperature comparison means (15) during heating operation will be explained. When the heating operation is started in step (20), the compressor (1) is started in step (21) at a preset frequency, and in step (22) the compressor (1) is started at a predetermined frequency. It is determined whether a time (for example, 3 minutes) has elapsed, and if it is less than a predetermined time, the process proceeds to step (25) and the discharge pressure detection device (8
) determines whether the detected pressure Pd is within the range of 1 sand pressure difference with respect to the control pressure Pc, and if it is within the control pressure range, proceeds to step (27) and maintains the frequency. . Further, in the judgment in step (25), if the detected pressure Pd is lower than the control pressure Pc by IK/cIj or more, the process proceeds to step (26), where the frequency is increased by a predetermined value, and the detected pressure Pd is lower than the control pressure Pc. Against I Kglc
If it is higher than d, proceed to step (28) and reduce the frequency by a predetermined value, and by repeating this operation, the detected pressure Pd will finally fall within a certain range with respect to the control pressure Pc. Then, the operating capacity of the compressor (1) is controlled. Incidentally, if a predetermined period of time has elapsed after starting the compressor (1) in step (22), the process proceeds to step (23), where the saturation temperature Tc is calculated by the saturation temperature conversion means (14) based on the detected pressure Pd. Proceeding to step (24), the temperature Td detected by the discharge temperature detection means (9) is compared with the saturation temperature Tc, and if Td is higher than Tc by 15 deg or more, the process proceeds to step (25), where the normal pressure-based frequency control −
Proceed to Chin. Further, in step (24), if the detected temperature Td does not have a difference of 15 de or more with respect to the saturation temperature Tc, the process proceeds to step (27), where the frequency is maintained and an increase in the operating capacity is prohibited. .
尚、ステップ（２２）で圧縮機（１）起動後所定時間が
経過しているか否かを判定しているのは、圧縮機（１）
の起動直後は検出温度Ｔｄは必ずしも十分に上昇しない
ので、誤動作により周波数が増加できないという不具合
を解消するものである。また、ステップ（２４）で、検
出温度ＴｄがＴｃに対して１５ｄｅｇ以上の差温かなく
ステップ（２７）で周波数を維持している間に、徐々に
検出温度Ｔｄが上昇すれば、ステップ（２５）に進んで
通常の周波数制御ルーチンに進む。In addition, in step (22), it is the compressor (1) that determines whether a predetermined time has elapsed after the compressor (1) was started.
This solves the problem that the frequency cannot be increased due to malfunction, since the detected temperature Td does not necessarily rise sufficiently immediately after startup. Further, if the detected temperature Td gradually increases in step (24) while maintaining the frequency in step (27) without a difference of 15 degrees or more with respect to Tc, step (25) to proceed with the normal frequency control routine.
また、冷房運転時の制御動作については特に説明しない
が、第２図に示す暖房時のフローチャートにかける、ス
テップ（２５）にかける判定が、蒸発温度検出装置（１
２）による検出温度が一定範囲内に入るか否かに変更さ
れ、所定温度以下の場合には周波数を減少、所定温度以
上の場合には周波数を増加するように制御するものであ
る。Further, although the control operation during cooling operation will not be particularly explained, the determination made in step (25) in the flowchart during heating shown in FIG.
2), the detected temperature is changed to determine whether it falls within a certain range, and control is performed so that if the temperature is below a predetermined temperature, the frequency is decreased, and if the temperature is above a predetermined temperature, the frequency is increased.
この発明は以上説明したとかり、圧縮容量調整可能な圧
縮機の吐出ガス温度を検出する吐出温度検出手段と、吐
出圧力を検出する吐出圧力検出手段と、前記吐出圧力検
出手段による検出圧力に相当する飽和温度を換算する飽
和温度換算手段と、吐出温度検出手段による検出温度と
上記飽和温度換算手段による飽和温度とを比較し、その
差温を検出する温度比較手段とを備え前記温度比較手段
による差温か所定値以下の場合には、上記圧縮機の圧縮
容量の増加を禁止するようにしたので、起動時に発生す
る液バツク状態で圧縮機が運転容量を増加させることが
なく、摺動部に加わる負荷を小さくすることが可能とな
り結果的に圧縮機の事故を未然に防ぐことができる。ま
た、通常運転時に発生する過渡的な液バツクが発生した
場合でも、圧縮機の運転容量の増加を禁止し、液バツク
が解消された後に圧縮機の運転容量を増加するように制
御しているので、圧縮機の運転状態を良好に保つことが
でき、空気調和機の信頼性を高めることが可能となる。As described above, the present invention includes a discharge temperature detection means for detecting the discharge gas temperature of a compressor whose compression capacity can be adjusted, a discharge pressure detection means for detecting discharge pressure, and a pressure detected by the discharge pressure detection means. and temperature comparison means for comparing the temperature detected by the discharge temperature detection means and the saturation temperature determined by the saturation temperature conversion means and detecting the difference in temperature. If the temperature difference is below a predetermined value, the compressor's compression capacity is prohibited from increasing. This prevents the compressor from increasing its operating capacity in the liquid back-up state that occurs at startup, and prevents the sliding parts from increasing. It is possible to reduce the applied load, and as a result, compressor accidents can be prevented. Additionally, even if a transient liquid backlog occurs during normal operation, the compressor's operating capacity is prohibited from increasing, and the compressor's operating capacity is controlled to be increased after the liquid backlog is resolved. Therefore, the operating condition of the compressor can be maintained in good condition, and the reliability of the air conditioner can be improved.
更に、圧縮機起動直後で吐出温度が十分上昇しない所定
時間は、吐出温度検出手段による検出温度と飽和温度に
よる圧縮機容量の増加禁止を無効化したことにより、起
動時に誤動作することもなく、空気調和機の能力を十分
に発揮させることができる。Furthermore, for a predetermined period of time immediately after the compressor is started when the discharge temperature does not rise sufficiently, the prohibition of increasing the compressor capacity based on the temperature detected by the discharge temperature detection means and the saturation temperature is disabled. The ability of the harmonizer can be fully demonstrated.
第１図は、この発明の一実施例による空気調和機の全体
構成図、第２図は同じく暖房運転時の制御動作を示すフ
ローチャート、第３図は従来の空気調和機の全体構成図
である。
図中、（１）は圧縮機、Ｇ２）は四方弁、（３）は室外
熱交換器、（４）は減圧装置、（５）は室内熱交換器、
（６）はアキュムレータ、（８）は吐出圧力検出手段、
（９）は吐出温度検出手段、（１３）は運転容量制御手
段、（１４）は飽和温度換算手段、（１５）は温度比較
手段である。
なお、各図中同一符号は同一または相当部分を示す。FIG. 1 is an overall configuration diagram of an air conditioner according to an embodiment of the present invention, FIG. 2 is a flow chart showing control operations during heating operation, and FIG. 3 is an overall configuration diagram of a conventional air conditioner. . In the figure, (1) is a compressor, G2) is a four-way valve, (3) is an outdoor heat exchanger, (4) is a pressure reducing device, (5) is an indoor heat exchanger,
(6) is an accumulator, (8) is a discharge pressure detection means,
(9) is a discharge temperature detection means, (13) is an operating capacity control means, (14) is a saturation temperature conversion means, and (15) is a temperature comparison means. Note that the same reference numerals in each figure indicate the same or corresponding parts.
Claims (2)
器、減圧装置、室内熱交換器、アキュムレータを配管接
続した冷媒回路、上記圧縮機の運転容量を制御する運転
容量制御手段、上記圧縮機の吐出ガス温度を検出する吐
出温度検出手段、上記圧縮機の吐出圧力を検出する吐出
圧力検出手段、前記吐出圧力検出手段による検出圧力に
相当する冷媒飽和温度を換算する飽和温度換算手段及び
上記吐出温度検出手段による検出温度と上記飽和温度換
算手段による飽和温度とを比較し、その差温を検出する
温度比較手段とを備え、前記温度比較手段による差温が
所定値以下の場合には運転容量制御手段による圧縮容量
の増加を禁止するようにしたことを特徴とする空気調和
機。(1) A compressor with adjustable compression capacity, a four-way valve, an outdoor heat exchanger, a pressure reducing device, an indoor heat exchanger, a refrigerant circuit in which an accumulator is connected via piping, an operating capacity control means for controlling the operating capacity of the compressor, and the above. Discharge temperature detection means for detecting the discharge gas temperature of the compressor; discharge pressure detection means for detecting the discharge pressure of the compressor; saturation temperature conversion means for converting a refrigerant saturation temperature corresponding to the pressure detected by the discharge pressure detection means; temperature comparison means for comparing the temperature detected by the discharge temperature detection means and the saturation temperature determined by the saturation temperature conversion means and detecting a temperature difference therebetween; An air conditioner characterized in that an increase in compression capacity by an operating capacity control means is prohibited.
る検出温度、飽和温度換算手段による飽和温度、並びに
温度比較手段による差温に基づく圧縮容量の増加禁止制
御を無効化するようにしたことを特徴とする請求項１記
載の空気調和機。(2) For a predetermined period of time after the compressor is started, the compression capacity increase prohibition control based on the temperature detected by the discharge temperature detection means, the saturation temperature by the saturation temperature conversion means, and the difference in temperature by the temperature comparison means is disabled. The air conditioner according to claim 1, characterized in that:
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19325489A JPH0781749B2 (en) | 1989-07-26 | 1989-07-26 | Air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP19325489A JPH0781749B2 (en) | 1989-07-26 | 1989-07-26 | Air conditioner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0359351A true JPH0359351A (en) | 1991-03-14 |
| JPH0781749B2 JPH0781749B2 (en) | 1995-09-06 |
Family
ID=16304898
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP19325489A Expired - Lifetime JPH0781749B2 (en) | 1989-07-26 | 1989-07-26 | Air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0781749B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5265436A (en) * | 1991-11-18 | 1993-11-30 | Sanyo Electric Co., Ltd. | Control apparatus for air-conditioners |
| JPH0640391U (en) * | 1992-10-30 | 1994-05-27 | 株式会社島津製作所 | Hydraulic unit |
| JP2014105986A (en) * | 2012-11-30 | 2014-06-09 | Panasonic Corp | Refrigerator |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3853550B2 (en) * | 1999-11-12 | 2006-12-06 | 三菱電機株式会社 | Air conditioner |
-
1989
- 1989-07-26 JP JP19325489A patent/JPH0781749B2/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5265436A (en) * | 1991-11-18 | 1993-11-30 | Sanyo Electric Co., Ltd. | Control apparatus for air-conditioners |
| JPH0640391U (en) * | 1992-10-30 | 1994-05-27 | 株式会社島津製作所 | Hydraulic unit |
| JP2014105986A (en) * | 2012-11-30 | 2014-06-09 | Panasonic Corp | Refrigerator |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0781749B2 (en) | 1995-09-06 |
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