JP5663345B2 - Refrigerant circuit with compressor abnormality detection function - Google Patents

Refrigerant circuit with compressor abnormality detection function Download PDF

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JP5663345B2
JP5663345B2 JP2011038689A JP2011038689A JP5663345B2 JP 5663345 B2 JP5663345 B2 JP 5663345B2 JP 2011038689 A JP2011038689 A JP 2011038689A JP 2011038689 A JP2011038689 A JP 2011038689A JP 5663345 B2 JP5663345 B2 JP 5663345B2
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refrigerant
temperature
compressor
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discharge
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JP2012172957A (en
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弘樹 成安
弘樹 成安
和樹 岩村
和樹 岩村
啓二 杉森
啓二 杉森
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Yanmar Co Ltd
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Description

本発明は、圧縮機の異常検知機能を備えた冷媒回路に関するものである。   The present invention relates to a refrigerant circuit having a compressor abnormality detection function.

従来より、冷媒回路において、冷媒の吐出温度の異常低下を検知する構成が開示されている（特許文献１参照）。   2. Description of the Related Art Conventionally, a configuration for detecting an abnormal drop in refrigerant discharge temperature in a refrigerant circuit has been disclosed (see Patent Document 1).

上記従来の冷媒回路は、吸入温度、吐出圧力および吸入圧力の検出値に基づき理論断熱圧縮吐出温度を算出し、この理論断熱圧縮吐出温度から所定値を減じた値を比較用吐出温度として、吐出温度の検出値と比較して異常低下を検知するようになされていた。   The conventional refrigerant circuit calculates the theoretical adiabatic compression discharge temperature based on the detected values of the suction temperature, the discharge pressure and the suction pressure, and uses a value obtained by subtracting a predetermined value from the theoretical adiabatic compression discharge temperature as a comparison discharge temperature. Compared with the detected value of temperature, an abnormal drop was detected.

特開２００８−２４１１２１号公報JP 2008-241121 A

ところで、上記従来の冷媒回路の場合、各検出値に基づき算出される理論断熱圧縮吐出温度は、断熱圧縮を前提としているが、実際の検出吐出温度は、軸受け摩擦等の圧縮機の機械的な運転損失によって発生する熱の影響も受けるため、理論断熱圧縮吐出温度よりも高温になる。このように、実際の検出吐出温度が理論断熱圧縮吐出温度よりも高温になったとしても、上記従来の冷媒回路は、実際の検出吐出温度の異常低下の検出が課題であるため、実際の検出吐出温度よりも低温の理論断熱圧縮吐出温度からさらに所定値を減じた比較用吐出温度を基準値としても、実際の検出吐出温度の異常低下の検出には何ら不都合は生じない。   By the way, in the case of the conventional refrigerant circuit, the theoretical adiabatic compression / discharge temperature calculated based on each detected value is premised on adiabatic compression, but the actual detected discharge temperature is the mechanical pressure of the compressor such as bearing friction. The temperature is higher than the theoretical adiabatic compression discharge temperature because it is also affected by the heat generated by the operating loss. Thus, even if the actual detected discharge temperature becomes higher than the theoretical adiabatic compression discharge temperature, the above conventional refrigerant circuit has a problem of detecting an abnormal drop in the actual detected discharge temperature. Even if a comparative discharge temperature obtained by further subtracting a predetermined value from the theoretical adiabatic compression discharge temperature lower than the discharge temperature is used as a reference value, there is no inconvenience in detecting an abnormal drop in the actual detected discharge temperature.

しかし、圧縮機の軸受けの異常摩擦や、隙間不良による異常接触などで圧縮機に異常な機械的損失を生じた場合は、機械的な運転損失によって発生する熱の影響がさらに増えるため、圧縮機異常時の検出吐出温度は、理論断熱圧縮吐出温度よりもさらに高温となる。   However, if abnormal mechanical loss occurs in the compressor due to abnormal friction of the bearing of the compressor or abnormal contact due to a gap defect, the effect of heat generated by mechanical operating loss further increases. The detected discharge temperature at the time of abnormality is higher than the theoretical adiabatic compression discharge temperature.

したがって、実際の検出吐出温度は、通常運転時も圧縮機異常時でも、断熱圧縮を前提とする理論断熱圧縮吐出温度よりも高温であるため、実際の検出吐出温度と、断熱圧縮を前提とする理論断熱圧縮吐出温度とを比較しただけでは、圧縮機の異常による検出吐出温度の異常上昇を検出することは非常に困難であった。   Therefore, the actual detected discharge temperature is higher than the theoretical adiabatic compression discharge temperature that assumes adiabatic compression, both during normal operation and when the compressor is abnormal. Only by comparing the theoretical adiabatic compression discharge temperature, it was very difficult to detect an abnormal rise in the detected discharge temperature due to an abnormality in the compressor.

本発明は係る実情に鑑みてなされたものであって、実際の吐出温度の異常上昇を検知するにあたり、断熱圧縮を前提とする理論値に圧縮機の運転効率を加味して圧縮機の異常検知を可能にする構成を提供する。   The present invention has been made in view of the actual situation, and in detecting an abnormal increase in actual discharge temperature, an abnormality in the compressor is detected by adding the operation efficiency of the compressor to a theoretical value on the premise of adiabatic compression. Provide a configuration that enables

上記課題を解決するための本発明の冷媒回路は、圧縮機の吐出経路に温度センサ、圧力センサを設け、吸入経路に温度センサ、圧力センサを設けた冷媒回路において、吐出経路の検知圧力および検知温度、吸入経路の検知圧力および検知温度に基づいて実際の運転効率を算出し、実際の運転効率が最低運転効率よりも所定値未満であるか否かを判定し、実際の運転効率が所定値未満であると判定した場合に圧縮機の異常を検知する制御部を有するものである。 The refrigerant circuit of the present invention to solve the above problems, the temperature sensor in the discharge path of the compressor, the pressure sensor is provided, the temperature sensor to the suction passage, the refrigerant circuit provided with a pressure sensor, the sensed pressure and sensed in the discharge path The actual operating efficiency is calculated based on the temperature, the detected pressure of the suction route, and the detected temperature, it is determined whether the actual operating efficiency is less than a predetermined value from the minimum operating efficiency, and the actual operating efficiency is a predetermined value. And a control unit that detects an abnormality of the compressor when it is determined that the value is less than .

以上述べたように、本発明によると、圧縮機の運転効率を加味した吐出温度の異常上昇の検知により圧縮機の機械的な不具合（圧縮機ロック、軸受け異常など）を早期に検知できる。   As described above, according to the present invention, mechanical malfunctions (compressor lock, bearing abnormality, etc.) of the compressor can be detected at an early stage by detecting an abnormal increase in the discharge temperature in consideration of the operation efficiency of the compressor.

本発明に係る冷媒回路の暖房時の冷媒の流れを示す回路図である。It is a circuit diagram which shows the flow of the refrigerant | coolant at the time of the heating of the refrigerant circuit which concerns on this invention. 本発明に係る冷媒回路の冷房時の冷媒の流れを示す回路図である。It is a circuit diagram which shows the flow of the refrigerant | coolant at the time of cooling of the refrigerant circuit which concerns on this invention. 本発明に係る冷媒回路の圧縮機部分の要部構成の概略を示す回路図である。It is a circuit diagram which shows the outline of the principal part structure of the compressor part of the refrigerant circuit which concerns on this invention. 本発明に係る冷媒回路において通常運転時と異常時とにおける圧縮機の吐出温度の違いを説明するモリエル線図である。It is a Mollier diagram explaining the difference of the discharge temperature of the compressor at the time of normal operation and abnormality at the refrigerant circuit which concerns on this invention. 本発明に係る冷媒回路の制御装置のブロック図である。It is a block diagram of the control apparatus of the refrigerant circuit which concerns on this invention.

以下、本発明の実施の形態を図面を参照して説明する。   Hereinafter, embodiments of the present invention will be described with reference to the drawings.

図１は冷媒回路１の暖房運転時の冷媒の流れを示し、図２は冷媒回路１の冷房運転時の冷媒の流れを示している。   FIG. 1 shows the refrigerant flow during the heating operation of the refrigerant circuit 1, and FIG. 2 shows the refrigerant flow during the cooling operation of the refrigerant circuit 1.

この冷媒回路１は、圧縮機１ａ，１ｂの吐出経路１１ａ，１１ｂに温度センサＳ１，Ｓ２を設け、共通の吐出経路１１に圧力センサＳ３を設け、吸入経路１２に温度センサＳ４、圧力センサＳ５を設け、圧力センサＳ３によって検知される吐出経路１１の検知圧力ＰＨ、圧力センサＳ５によって検知される吸入経路の検知圧力ＰＬ、温度センサＳ１２によって検知される吸入経路の検知温度ＴＳ４に基づいて理論断熱圧縮冷媒吐出温度ＴＤ１ｔ，ＴＤ２ｔを算出し、吐出経路１１ａ，１１ｂの検知冷媒吐出温度ＴＤ１，ＴＤ２が理論断熱圧縮冷媒吐出温度ＴＤ１ｔ，ＴＤ２ｔよりも所定値以上の高温冷媒吐出温度ＴＤ１ｒ，ＴＤ２ｒであるか否かを判定し、所定値以上の高温冷媒吐出温度ＴＤ１ｒ，ＴＤ２ｒであると判定した場合に圧縮機１ａ，１ｂが異常であることを検知するように構成されている。   The refrigerant circuit 1 includes temperature sensors S1 and S2 in the discharge paths 11a and 11b of the compressors 1a and 1b, a pressure sensor S3 in the common discharge path 11, and a temperature sensor S4 and a pressure sensor S5 in the suction path 12. Theoretical adiabatic compression based on the detected pressure PH of the discharge path 11 detected by the pressure sensor S3, the detected pressure PL of the suction path detected by the pressure sensor S5, and the detected temperature TS4 of the suction path detected by the temperature sensor S12 The refrigerant discharge temperatures TD1t and TD2t are calculated, and whether or not the detected refrigerant discharge temperatures TD1 and TD2 of the discharge paths 11a and 11b are higher than the theoretical adiabatic compression refrigerant discharge temperatures TD1t and TD2t by a predetermined value or higher. If it is determined that the high-temperature refrigerant discharge temperatures TD1r and TD2r are equal to or higher than a predetermined value, the compressor 1 , And it is configured to detect that 1b is abnormal.

温度センサＳ１，Ｓ２は、各圧縮機１ａ、１ｂの吐出口から共通の吐出経路１１に到る吐出経路１１ａ、１１ｂ上であれば、何処に設けてもよい。圧縮機１ａ，１ｂが一台しか動いていない場合には、共通の吐出経路１１に設けた温度センサＳ１１によって測定される検知冷媒吐出温度ＴＤを、運転中の圧縮機１ａ，１ｂの吐出経路１１ａ、１１ｂに設けられた温度センサＳ１またはＳ２の検知冷媒吐出温度ＴＤ１，ＴＤ２としてもよい。   The temperature sensors S1 and S2 may be provided anywhere on the discharge paths 11a and 11b from the discharge ports of the compressors 1a and 1b to the common discharge path 11. When only one compressor 1a, 1b is moving, the detected refrigerant discharge temperature TD measured by the temperature sensor S11 provided in the common discharge path 11 is used as the discharge path 11a of the compressors 1a, 1b during operation. , 11b may be detected refrigerant discharge temperatures TD1, TD2 of the temperature sensor S1 or S2.

圧力センサＳ３は、圧縮機１ａ，１ｂの吐出口から四方弁６に到る吐出経路１１ａ、１１ｂまたは１１上であれば、何処に設けてもよい。図１および図２では、吐出経路１１ａと１１ｂの合流点からオイルセパレータ２へ至るまでの共通の吐出経路１１で測定している。この場合、オイルセパレータ２での圧力損失の影響を受けず、測定位置としては好ましい。   The pressure sensor S3 may be provided anywhere as long as it is on the discharge path 11a, 11b or 11 from the discharge ports of the compressors 1a and 1b to the four-way valve 6. In FIG. 1 and FIG. 2, the measurement is performed on the common discharge path 11 from the junction of the discharge paths 11 a and 11 b to the oil separator 2. In this case, it is not affected by the pressure loss in the oil separator 2 and is preferable as a measurement position.

温度センサＳ１２は、アキュームレータ３の下流で圧縮機１ａ、１ｂの吸入口への分岐前であれば、吸入経路１２の何処に設けてもよい。図１および図２では、吸入経路１２に設けられたアキュームレータ３の下流のオイルセパレータ２からのオイル戻しライン１８の合流点よりも下流で圧縮機１ａ、１ｂの吸入口への分岐前に設けられている。この場合、圧縮機１ａ、１ｂの吸入直前の冷媒温度を測定できるので、理論断熱圧縮温度ＴＤ１ｔ,ＴＤｔ２の算出精度が高まり、測定位置としては好ましい。   The temperature sensor S12 may be provided anywhere in the suction path 12 as long as it is downstream of the accumulator 3 and before branching to the suction ports of the compressors 1a and 1b. In FIG. 1 and FIG. 2, it is provided before branching to the suction ports of the compressors 1 a and 1 b downstream from the junction of the oil return line 18 from the oil separator 2 downstream of the accumulator 3 provided in the suction path 12. ing. In this case, since the refrigerant temperature immediately before the suction of the compressors 1a and 1b can be measured, the calculation accuracy of the theoretical adiabatic compression temperatures TD1t and TDt2 is increased, which is preferable as a measurement position.

圧力センサＳ５は、四方弁６から圧縮機１ａ、１ｂの吸入口に到る吸入経路１２の何処に設けてもよい。図１および図２では、吸入経路１２に設けられたアキュームレータ３よりも上流側に設けられている。この場合、アキュームレータ３での圧力損失の影響を受けず、測定位置としては好ましい。   The pressure sensor S5 may be provided anywhere in the suction path 12 from the four-way valve 6 to the suction ports of the compressors 1a and 1b. In FIG. 1 and FIG. 2, it is provided upstream of the accumulator 3 provided in the suction path 12. In this case, it is not affected by the pressure loss in the accumulator 3, and is preferable as a measurement position.

この冷媒回路１は、冷房運転時は圧縮機１ａ，１ｂの吐出ライン１１を室外熱交換器４ａ，４ｂに接続するとともに圧縮機１ａ，１ｂの吸入ライン１２を室内熱交換器５に接続し、暖房運転時は圧縮機１ａ，１ｂの吐出ライン１１を室内熱交換器５に接続するとともに圧縮機１ａ，１ｂの吸入ライン１２を室外熱交換器４ａ，４ｂに接続する四方弁６を設け、圧縮機１ａ，１ｂを駆動するエンジン（図示省略）を設け、室外熱交換器４ａ，４ｂと室内熱交換器５を接続する液管ライン１３にレシーバ７を設け、暖房運転時におけるレシーバ７の下流に室外熱交換器４ａ，４ｂと並列にエンジン冷却水によるサブエバポレータ８を設け、サブエバポレータ８の下流ライン１４を四方弁６から圧縮機吸入口に至る吸入ライン１２に接続し、室外熱交換器４ａ，４ｂとレシーバ７の接続ライン１５に第１室外電動膨張弁ＥＶ１を設け、サブエバポレータ８とレシーバ７の接続ライン１６に第２室外電動膨張弁ＥＶ２を設け、サブエバポレータ８の下流ライン１４と四方弁６から圧縮機吸入口に至る吸入ライン１２の接続部下流の冷媒過熱度に基づいて第１室外電動膨張弁ＥＶ１の開度を制御するようになされている。   During the cooling operation, the refrigerant circuit 1 connects the discharge lines 11 of the compressors 1a and 1b to the outdoor heat exchangers 4a and 4b and connects the suction lines 12 of the compressors 1a and 1b to the indoor heat exchanger 5, During the heating operation, a four-way valve 6 is provided to connect the discharge lines 11 of the compressors 1a and 1b to the indoor heat exchanger 5 and connect the suction lines 12 of the compressors 1a and 1b to the outdoor heat exchangers 4a and 4b. An engine (not shown) for driving the machines 1a and 1b is provided, a receiver 7 is provided in the liquid pipe line 13 connecting the outdoor heat exchangers 4a and 4b and the indoor heat exchanger 5, and downstream of the receiver 7 during heating operation. A sub-evaporator 8 made of engine cooling water is provided in parallel with the outdoor heat exchangers 4a and 4b, and a downstream line 14 of the sub-evaporator 8 is connected to a suction line 12 extending from the four-way valve 6 to the compressor suction port so that the outdoor heat A first outdoor electric expansion valve EV1 is provided in the connection line 15 between the exchangers 4a and 4b and the receiver 7, a second outdoor electric expansion valve EV2 is provided in the connection line 16 between the sub-evaporator 8 and the receiver 7, and the downstream line of the sub-evaporator 8 is provided. 14 and the opening degree of the first outdoor electric expansion valve EV1 is controlled based on the degree of refrigerant superheating downstream of the connection portion of the suction line 12 from the four-way valve 6 to the compressor suction port.

まず、この冷媒回路１の暖房時および冷房時における冷媒およびオイルの流れについて説明する。   First, the flow of refrigerant and oil during heating and cooling of the refrigerant circuit 1 will be described.

冷媒回路１において、圧縮機１ａ、１ｂで圧縮した冷媒は、当該圧縮機１ａ、１ｂからの吐出ライン１１を介してオイルセパレータ２に導入され、冷媒とオイルに分離される。   In the refrigerant circuit 1, the refrigerant compressed by the compressors 1a and 1b is introduced into the oil separator 2 through the discharge line 11 from the compressors 1a and 1b, and is separated into refrigerant and oil.

このうち、図１に示すように、暖房運転の場合、冷媒は、四方弁６を介して室内熱交換器５で放熱して凝縮液化した後、ブリッジ回路９を経てレシーバ７に貯留される。この液冷媒は、再度ブリッジ回路９を経て電動膨張弁ＥＶ１の開度調整により、室外熱交換器４ａ，４ｂで蒸発気化した後、アキュームレータ３に入る。この際、冷媒は、圧縮機１ａ，１ｂへの吸入ライン１２に設けた圧力センサＳ５から冷媒の飽和蒸気圧温度を算出し、この算出温度よりもアキュームレータ３に入る手前の温度センサＳ４から測定される実際の冷媒の温度が所定温度以上の過熱度を維持するように電動膨張弁ＥＶ１の開度が制御されて供給される。これにより、アキュームレータ３での液バックを監視できる。   Among these, as shown in FIG. 1, in the heating operation, the refrigerant radiates heat in the indoor heat exchanger 5 through the four-way valve 6 to be condensed and liquefied, and then is stored in the receiver 7 through the bridge circuit 9. The liquid refrigerant passes through the bridge circuit 9 again and is evaporated and evaporated in the outdoor heat exchangers 4a and 4b by adjusting the opening degree of the electric expansion valve EV1, and then enters the accumulator 3. At this time, the refrigerant calculates the saturated vapor pressure temperature of the refrigerant from the pressure sensor S5 provided in the suction line 12 to the compressors 1a and 1b, and is measured from the temperature sensor S4 before entering the accumulator 3 from the calculated temperature. The opening degree of the electric expansion valve EV1 is controlled and supplied so that the actual refrigerant temperature maintains a superheat degree equal to or higher than a predetermined temperature. Thereby, the liquid back | bag in the accumulator 3 can be monitored.

それでも、このアキュームレータ３に入る手前の温度センサＳ４から測定される実際の冷媒の過熱度が所定温度未満の場合は、電動膨張弁ＥＶ１の開度を絞る。また、外気温度が低く、室外熱交換器４ａ、４ｂで冷媒を十分に蒸発できない場合は、電動膨張弁ＥＶ２の開度制御によりサブエバポレータ８へと冷媒を流し、当該サブエバポレータ８においてエンジン（図示省略）の廃熱によって充分に過熱されたガス冷媒としてからアキュームレータ３に供給される。この際、サブエバポレータ８を経て供給される冷媒の温度は温度センサＳ７によって測定される。
ここで、冷媒を室外熱交換器４ａ、４ｂとサブエバポレータ８の両方を使用する場合は、電動膨張弁ＥＶ２の開度制御は、温度センサＳ７から測定される実際の冷媒の温度が温度センサＳ４から測定される実際の冷媒温度よりも所定温度以上となるように行われる。こうすることで、電動膨張弁ＥＶ１の開度を保ちながら、即ち、室外熱交換器４ａ、４ｂへの冷媒流量を確保してサブエバポレータ８での圧損を抑えながら、合流後の冷媒の過熱度を所定温度に維持できる。 Still, when the actual superheat degree of the refrigerant measured from the temperature sensor S4 before entering the accumulator 3 is lower than the predetermined temperature, the opening degree of the electric expansion valve EV1 is reduced. Further, when the outdoor air temperature is low and the outdoor heat exchangers 4a and 4b cannot sufficiently evaporate the refrigerant, the refrigerant is caused to flow to the sub-evaporator 8 by controlling the opening degree of the electric expansion valve EV2, and the sub-evaporator 8 performs engine (illustration). It is supplied to the accumulator 3 after being sufficiently heated by the waste heat (not shown). At this time, the temperature of the refrigerant supplied through the sub-evaporator 8 is measured by the temperature sensor S7.
Here, when both the outdoor heat exchangers 4a and 4b and the sub-evaporator 8 are used as the refrigerant, the opening degree control of the electric expansion valve EV2 is based on the actual refrigerant temperature measured from the temperature sensor S7. It is performed so that it may become more than predetermined temperature rather than the actual refrigerant | coolant temperature measured from. In this way, while maintaining the opening degree of the electric expansion valve EV1, that is, while ensuring the refrigerant flow rate to the outdoor heat exchangers 4a and 4b and suppressing the pressure loss in the sub-evaporator 8, the degree of superheat of the refrigerant after merging Can be maintained at a predetermined temperature.

その後、冷媒は、アキュームレータ３から冷媒の吸入ライン１２を通って再度圧縮機１ａ、１ｂへと吸引される。   Thereafter, the refrigerant is sucked again from the accumulator 3 through the refrigerant suction line 12 to the compressors 1a and 1b.

一方、オイルは、オイルセパレータ２の底部からのオイル戻しライン１７に設けられたキャピラリＣＴ０または開閉弁ＳＶ０を経た後、開閉弁ＳＶ１，ＳＶ２、キャピラリＣＴ１，ＣＴ２、オイル温度センサＳ８，Ｓ９を経て圧縮機１ａ、１ｂへと返送される。また、オイルセパレータ２内の油面付近のオイルは、オイル戻しライン１８から開閉弁ＳＶ３、キャピラリＣＴ３、オイル温度センサＳ１０を経て冷媒の吸入ライン１２から圧縮機１ａ，１ｂへと返送される。   On the other hand, the oil passes through the capillary CT0 or the on-off valve SV0 provided in the oil return line 17 from the bottom of the oil separator 2, and then is compressed through the on-off valves SV1, SV2, capillaries CT1, CT2, and oil temperature sensors S8, S9. Returned to machine 1a, 1b. The oil in the vicinity of the oil level in the oil separator 2 is returned from the oil return line 18 to the compressors 1a and 1b from the refrigerant suction line 12 via the on-off valve SV3, capillary CT3, and oil temperature sensor S10.

冷房運転の場合、図２に示すように、冷媒は、四方弁６を介して室外熱交換器４ａ，４ｂで放熱して凝縮液化した後、レシーバ７に貯留される。この液冷媒は、ブリッジ回路９を経て電動膨張弁５１の開度調整により、室内熱交換器５で蒸発気化した後、アキュームレータ３に入る。このアキュームレータ３に入ったガス冷媒の過熱度が小さすぎる場合は、電動膨張弁ＥＶ２の開度制御によりサブエバポレータ８へと冷媒を流し、当該サブエバポレータ８においてエンジン（図示省略）の廃熱によって充分に過熱されたガス冷媒としてからアキュームレータ３に供給される。   In the case of the cooling operation, as shown in FIG. 2, the refrigerant radiates heat in the outdoor heat exchangers 4 a and 4 b through the four-way valve 6 to be condensed and liquefied, and is then stored in the receiver 7. This liquid refrigerant evaporates and evaporates in the indoor heat exchanger 5 by adjusting the opening degree of the electric expansion valve 51 through the bridge circuit 9 and then enters the accumulator 3. When the degree of superheat of the gas refrigerant that has entered the accumulator 3 is too small, the refrigerant is caused to flow to the sub-evaporator 8 by controlling the opening degree of the electric expansion valve EV2, and the sub-evaporator 8 is sufficient due to the waste heat of the engine (not shown). Is supplied to the accumulator 3 after being heated as a gas refrigerant.

この場合もオイルは、オイル戻しライン１７に設けられたキャピラリＣＴ０または開閉弁ＳＶ０を経た後、開閉弁ＳＶ１，ＳＶ２、キャピラリＣＴ１，ＣＴ２、オイル温度センサＳ８，Ｓ９を経て圧縮機１ａ、１ｂへと返送される。また、オイルセパレータ２内の油面付近のオイルは、オイル戻しライン１８から開閉弁ＳＶ３、キャピラリＣＴ３、オイル温度センサＳ１０を経て冷媒の吸入ライン１２から圧縮機１ａ，１ｂへと返送される。   Also in this case, the oil passes through the capillary CT0 or the on-off valve SV0 provided in the oil return line 17, and then goes to the compressors 1a and 1b through the on-off valves SV1 and SV2, capillaries CT1 and CT2, and oil temperature sensors S8 and S9. Will be returned. The oil in the vicinity of the oil level in the oil separator 2 is returned from the oil return line 18 to the compressors 1a and 1b from the refrigerant suction line 12 via the on-off valve SV3, capillary CT3, and oil temperature sensor S10.

なお、圧縮機１ａ，１ｂは、一台のみで運転する場合もあれば、二台ともに運転する場合もある。一台のみの運転の場合は、開閉弁ＳＶ２が閉じられて圧縮機１ｂへのオイルの供給が停止され、圧縮機１ａのみの運転となる。この場合、圧縮機１ａから吐出された冷媒は、圧縮機１ｂの吐出口下流に設けられた逆止弁ＣＶ１によって圧縮機１ｂへの逆流が防止される。開閉弁ＳＶ１，ＳＶ２の開閉は、それぞれ、圧縮機１ａ，１ｂの発停に連動するようになされている。   The compressors 1a and 1b may be operated by only one unit, or may be operated by both units. In the case of operation of only one unit, the on-off valve SV2 is closed, the supply of oil to the compressor 1b is stopped, and only the compressor 1a is operated. In this case, the refrigerant discharged from the compressor 1a is prevented from flowing back to the compressor 1b by the check valve CV1 provided downstream of the discharge port of the compressor 1b. Opening and closing of the on-off valves SV1 and SV2 is interlocked with the start and stop of the compressors 1a and 1b, respectively.

また、上記図１および図２において、冷媒回路１は、一台の室外機Ａに対して一台の室内機Ｂしか接続されていないが、閉鎖弁ＢＶ１とＢＶ２との間に複数台の室内機Ｂが接続可能となされている。また、圧縮機１ａ，１ｂは、これら接続された室内機Ｂの運転状況に応じて１台または２台以上が運転される。   1 and 2, the refrigerant circuit 1 has only one indoor unit B connected to one outdoor unit A, but a plurality of indoor units B are provided between the closing valves BV1 and BV2. Machine B can be connected. Further, one or two or more compressors 1a and 1b are operated according to the operation status of the connected indoor units B.

上記構成において、本発明の冷媒回路１の制御装置１０は、圧縮機１ａ，１ｂの異常を検知することができるようになされている。   In the above configuration, the control device 10 of the refrigerant circuit 1 according to the present invention can detect an abnormality in the compressors 1a and 1b.

図３は冷媒回路１のうち、圧縮機１ａ周辺の概略を示し、図４は同圧縮機１ａの異常検知を説明するモリエル線図を示し、図５は圧縮機１ａの異常を検知する制御装置１０のブロック図を示している。以下において、説明の便宜上、圧縮機１ａが運転し、圧縮機１ｂが停止している状態を仮定して圧縮機１ａの異常検知について説明する。   FIG. 3 schematically shows the periphery of the compressor 1a in the refrigerant circuit 1, FIG. 4 shows a Mollier diagram for explaining abnormality detection of the compressor 1a, and FIG. 5 shows a control device for detecting abnormality of the compressor 1a. 10 block diagrams are shown. In the following, for convenience of explanation, the abnormality detection of the compressor 1a will be described on the assumption that the compressor 1a is operating and the compressor 1b is stopped.

圧縮機１ａの異常を検知する制御装置１０には、圧縮機１ａの吐出経路１１ａに設けた温度センサＳ１からの検知冷媒吐出温度ＴＤ１と、吐出経路１１に設けた圧力センサＳ３からの検知吐出圧力ＰＨと、吸入経路１２に設けた圧力センサＳ５からの検知吸入圧力ＰＬと、吸入経路１２に設けた温度センサＳ１２からの検知吸入温度ＴＳ４とが入力され、これらの入力情報に基づいて圧縮機１ａの異常を検知するように構成されている。   The controller 10 that detects an abnormality in the compressor 1a includes a detected refrigerant discharge temperature TD1 from the temperature sensor S1 provided in the discharge path 11a of the compressor 1a and a detected discharge pressure from the pressure sensor S3 provided in the discharge path 11. PH, a detected suction pressure PL from the pressure sensor S5 provided in the suction path 12, and a detected suction temperature TS4 from the temperature sensor S12 provided in the suction path 12 are input, and the compressor 1a is based on these input information. It is configured to detect abnormalities.

制御装置１０では、まず、実際の検知冷媒吐出温度ＴＤ１が、理論断熱圧縮冷媒吐出温度ＴＤ１ｔよりも異常に高温ＴＤ１ｒであるか否かを判定する。その方法としては、図４に示すように、検知吐出圧力ＰＨ、検知吸入圧力ＰＬおよび検知吸入温度ＴＳ４に基づいて圧縮機１ａの理論断熱圧縮冷媒吐出温度ＴＤ１ｔを算出する。ついで、この算出された理論断熱圧縮冷媒吐出温度ＴＤ１ｔに圧縮機１ａの最低運転効率を考慮した通常運転での最高冷媒吐出温度ＴＤ１ｒに換算する。そして、制御装置１０では、実際の検知冷媒吐出温度ＴＤ１が、理論断熱圧縮冷媒吐出温度ＴＤ１ｔから、最低運転効率で換算した通常運転での最高冷媒吐出温度ＴＤ１ｒまでの範囲内に有るか否かを判定する。   In the control device 10, first, it is determined whether or not the actual detected refrigerant discharge temperature TD1 is abnormally higher than the theoretical adiabatic compression refrigerant discharge temperature TD1t. As the method, as shown in FIG. 4, the theoretical adiabatic compressed refrigerant discharge temperature TD1t of the compressor 1a is calculated based on the detected discharge pressure PH, the detected intake pressure PL, and the detected intake temperature TS4. Subsequently, the calculated theoretical adiabatic compression refrigerant discharge temperature TD1t is converted into the maximum refrigerant discharge temperature TD1r in the normal operation in consideration of the minimum operation efficiency of the compressor 1a. Then, in the control device 10, it is determined whether or not the actual detected refrigerant discharge temperature TD1 is within the range from the theoretical adiabatic compression refrigerant discharge temperature TD1t to the maximum refrigerant discharge temperature TD1r in the normal operation converted by the minimum operation efficiency. judge.

実際の検知冷媒吐出温度ＴＤ１が、この範囲内にある場合、制御装置１０は、圧縮機１ａが通常運転時と判断し、あらかじめ設定した時間毎に上記した判定を繰り返す。   When the actual detected refrigerant discharge temperature TD1 is within this range, the control device 10 determines that the compressor 1a is in a normal operation, and repeats the above determination every preset time.

実際の検知冷媒吐出温度ＴＤ１が、この範囲よりも高温である場合、圧縮機１ａ内部の異常摩擦や異常接触により発生した熱によって冷媒が高温になったものと判断し、制御装置１０は、運転中の圧縮機１ａが異常運転時であると判断する。   When the actual detected refrigerant discharge temperature TD1 is higher than this range, the controller 10 determines that the refrigerant has become hot due to heat generated by abnormal friction or abnormal contact inside the compressor 1a. It is determined that the compressor 1a in the middle is in abnormal operation.

圧縮機１ａが異常運転時であると判断された場合は、その後、圧縮機１ａが停止され、圧縮機１ｂの運転に切り替えられるものであってもよいし、圧縮機１ａの停止により冷媒回路１全体を停止させるものであってもよいし、圧縮機１ａの異常をアラームやランプで知らせるようにしてもよい。   When it is determined that the compressor 1a is in an abnormal operation, the compressor 1a may be stopped and then switched to the operation of the compressor 1b, or the refrigerant circuit 1 may be stopped by stopping the compressor 1a. The whole may be stopped, or an abnormality of the compressor 1a may be notified by an alarm or a lamp.

なお、上記では、実際の検知冷媒吐出温度ＴＤ１が、理論断熱圧縮冷媒吐出温度ＴＤ１ｔから最低運転効率で換算した通常運転での最高冷媒吐出温度ＴＤ１ｒまでの範囲内に有るか否か、その温度差によって判定しているが、実際の検知冷媒吐出温度ＴＤ１と、理論断熱圧縮冷媒吐出温度ＴＤ１ｔとを比較した比率によって判定してもよい。すなわち、理論断熱圧縮冷媒吐出温度ＴＤ１ｔの場合の圧縮機１ａの運転効率を１００とし、この理論断熱冷媒吐出温度ＴＤ１ｔと、実際の検知冷媒吐出温度ＴＤ１との比率から、検知冷媒吐出温度ＴＤ１の場合の圧縮機１ａの実際の運転効率を求める。この実際の運転効率が、あらかじめ設定した運転効率、例えば、１００〜７５％に有るか否かを判定する。制御装置１０は、この範囲内の比率に納まっている場合、通常運転時と判断し、あらかじめ設定した時間毎に上記の判定を繰り返す。最低運転効率よりも所定値未満であれば、圧縮機１ａの異常と判断し、制御装置１０は、運転中の圧縮機１ａの停止指令を出力する。   In the above description, whether or not the actual detected refrigerant discharge temperature TD1 is within the range from the theoretical adiabatic compression refrigerant discharge temperature TD1t to the maximum refrigerant discharge temperature TD1r in the normal operation converted by the minimum operation efficiency, and the temperature difference therebetween. However, the actual detected refrigerant discharge temperature TD1 and the theoretical adiabatic compression refrigerant discharge temperature TD1t may be determined based on a ratio. That is, when the operation efficiency of the compressor 1a at the theoretical adiabatic compressed refrigerant discharge temperature TD1t is 100, the ratio of the theoretical adiabatic refrigerant discharge temperature TD1t to the actual detected refrigerant discharge temperature TD1 is the case of the detected refrigerant discharge temperature TD1. The actual operating efficiency of the compressor 1a is determined. It is determined whether or not the actual operation efficiency is a preset operation efficiency, for example, 100 to 75%. When the control device 10 falls within the ratio within this range, the control device 10 determines that the operation is normal, and repeats the above determination every preset time. If it is less than the predetermined value below the minimum operating efficiency, it is determined that the compressor 1a is abnormal, and the control device 10 outputs a stop command for the compressor 1a during operation.

この制御装置１０を備えた冷媒回路１によると、圧縮機１ａ，１ｂが完全に故障（いわゆるロック状態）になる前に、圧縮機１ａ，１ｂを停止させることができる。すなわち、圧縮機１ａ，１ｂの軸受け異常や隙間不良による異常接触などの機械的損失が発生した場合、これによる発熱の影響で冷媒の吐出温度が上昇する。ここで、通常は、冷媒の吐出温度が上昇すると、運転継続をさせるために、液インジェクションなどの過熱防止制御が開始されてしまって、異常が発生した圧縮機１ａ、１ｂの運転が継続される。したがって、圧縮機１ａ，１ｂのこのような機械的損失による異常は、圧縮機１ａ，１ｂが完全に故障するまで見逃され易く、その結果、完全故障後からの復旧に手間を要していた。   According to the refrigerant circuit 1 including the control device 10, the compressors 1a and 1b can be stopped before the compressors 1a and 1b are completely broken (so-called locked state). That is, when a mechanical loss such as an abnormal contact due to a bearing abnormality of the compressors 1a and 1b or a gap defect occurs, the discharge temperature of the refrigerant rises due to the heat generated by this. Here, normally, when the discharge temperature of the refrigerant rises, overheat prevention control such as liquid injection is started to continue the operation, and the operation of the compressors 1a and 1b in which an abnormality has occurred is continued. . Therefore, the abnormality due to such mechanical loss of the compressors 1a and 1b is easily overlooked until the compressors 1a and 1b completely fail, and as a result, it takes time to recover after the complete failure.

しかし、この制御装置１０を備えた冷媒回路１によると、機械的損失によって冷媒の吐出温度が上昇したタイミングで圧縮機１ａ，１ｂの異常を検知することができるので、圧縮機１ａ，１ｂの完全故障を防止し、復旧作業の容易化を図ることができる。   However, according to the refrigerant circuit 1 provided with the control device 10, the abnormality of the compressors 1a and 1b can be detected at the timing when the refrigerant discharge temperature rises due to mechanical loss. Failure can be prevented and recovery work can be facilitated.

なお、上記では、圧縮機１ａの異常を検知する場合について述べているが、圧縮機１ｂの異常を検知する場合も同様である。さらに、圧縮機１ａ，１ｂの二台同時運転時に二台の圧縮機１ａ，１ｂの異常を検知する場合も同様である。   In addition, although the case where abnormality of the compressor 1a is detected is described above, the same applies to the case where abnormality of the compressor 1b is detected. Further, the same applies to the case where the abnormality of the two compressors 1a and 1b is detected during the simultaneous operation of the two compressors 1a and 1b.

また、圧縮機１ａ，１ｂは、３台以上の場合であってもよい。   The compressors 1a and 1b may be three or more.

さらに、上記冷媒回路１における圧縮機１ａの異常を検知する制御装置１０は、その制御プログラムを、既設の冷媒回路１の制御装置１０にインストールすることで、当該既設の冷媒回路１であっても、上記と同様に圧縮機１ａ，１ｂの異常を検知することができることとなる。ただし、制御プログラムの実行には、温度センサＳ１，Ｓ２，Ｓ１２、圧力センサＳ３，Ｓ５からの情報が必要となるため、既設の冷媒回路１にこれらのセンサが無い場合は、これらセンサの取り付けが必要となる。   Furthermore, the control device 10 that detects the abnormality of the compressor 1a in the refrigerant circuit 1 installs the control program in the control device 10 of the existing refrigerant circuit 1, so that the existing refrigerant circuit 1 can be installed. In the same manner as described above, the abnormality of the compressors 1a and 1b can be detected. However, since execution of the control program requires information from the temperature sensors S1, S2, S12 and the pressure sensors S3, S5, if these sensors are not present in the existing refrigerant circuit 1, these sensors must be attached. Necessary.

本発明に係る冷媒回路は、圧縮機を有する冷媒回路を用いた各種空調装置に使用される。   The refrigerant circuit according to the present invention is used in various air conditioners using a refrigerant circuit having a compressor.

１ 冷媒回路
１０ 制御部（制御装置）
１１ 吐出経路
１２ 吸入経路
Ｓ１ 温度センサ（ＴＤ１検知用）
Ｓ２ 温度センサ（ＴＤ２検知用）
Ｓ３ 圧力センサ（ＰＨ検知用）
Ｓ１２ 温度センサ（ＴＳ４検知用）
Ｓ５ 圧力センサ（ＰＬ検知用）
ＴＤ１ 圧縮機１ａの吐出冷媒の検知温度
ＴＤ２ 圧縮機１ｂの吐出冷媒の検知温度
ＴＳ４ 圧縮機１ａ、１ｂの吸入直前の冷媒検知温度
ＰＬ 吸入経路の検知圧力
ＰＨ 吐出経路の検知圧力
ＴＤ１ｔ 理論断熱圧縮冷媒吐出温度
ＴＤ２ｔ 理論断熱圧縮冷媒吐出温度
ＴＤ１ｒ 通常運転での最高冷媒吐出温度
ＴＤ２ｒ 通常運転での最高冷媒吐出温度 1 Refrigerant Circuit 10 Control Unit (Control Device)
11 Discharge path 12 Suction path S1 Temperature sensor (for TD1 detection)
S2 Temperature sensor (for TD2 detection)
S3 Pressure sensor (for PH detection)
S12 Temperature sensor (for TS4 detection)
S5 Pressure sensor (for PL detection)
TD1 Detected temperature of refrigerant discharged from compressor 1a TD2 Detected temperature of refrigerant discharged from compressor 1b TS4 Refrigerant detected temperature just before suction of compressors 1a, 1b PL Detected pressure of suction path PH Detected pressure of discharge path TD1t Theoretical adiabatic compressed refrigerant Discharge temperature TD2t Theoretical adiabatic compression refrigerant discharge temperature TD1r Maximum refrigerant discharge temperature TD2r in normal operation Maximum refrigerant discharge temperature in normal operation

Claims (1)

圧縮機の吐出経路に温度センサ、圧力センサを設け、吸入経路に温度センサ、圧力センサを設けた冷媒回路において、
吐出経路の検知圧力および検知温度、吸入経路の検知圧力および検知温度に基づいて実際の運転効率を算出し、
実際の運転効率が最低運転効率よりも所定値未満であるか否かを判定し、
実際の運転効率が所定値未満であると判定した場合に圧縮機の異常を検知する制御部を有することを特徴とする冷媒回路。 In a refrigerant circuit provided with a temperature sensor and a pressure sensor in the discharge path of the compressor, and provided with a temperature sensor and a pressure sensor in the suction path,
Calculate the actual operating efficiency based on the detection pressure and temperature of the discharge path, the detection pressure and temperature of the suction path,
Determine whether the actual driving efficiency is less than the predetermined value than the minimum driving efficiency,
A refrigerant circuit comprising a control unit that detects an abnormality of a compressor when it is determined that actual operation efficiency is less than a predetermined value .
JP2011038689A 2011-02-24 2011-02-24 Refrigerant circuit with compressor abnormality detection function Active JP5663345B2 (en)

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Publication number Priority date Publication date Assignee Title
CN111023418A (en) * 2019-12-26 2020-04-17 宁波奥克斯电气股份有限公司 Pressure sensor abnormity control method and device and air conditioner

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DE102021211280B4 (en) 2021-10-06 2023-05-04 Glen Dimplex Deutschland Gmbh Method and device for monitoring a refrigerant system

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JPS5692051U (en) * 1979-12-19 1981-07-22
JPH11248299A (en) * 1998-02-27 1999-09-14 Kawasaki Steel Corp Abnormality decision method for air compressor
JP2008241121A (en) * 2007-03-27 2008-10-09 Sanyo Electric Co Ltd Malfunction detecting device, malfunction detecting method and control program

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111023418A (en) * 2019-12-26 2020-04-17 宁波奥克斯电气股份有限公司 Pressure sensor abnormity control method and device and air conditioner

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