JP5171022B2 - Air conditioner - Google Patents

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JP5171022B2
JP5171022B2 JP2006338624A JP2006338624A JP5171022B2 JP 5171022 B2 JP5171022 B2 JP 5171022B2 JP 2006338624 A JP2006338624 A JP 2006338624A JP 2006338624 A JP2006338624 A JP 2006338624A JP 5171022 B2 JP5171022 B2 JP 5171022B2
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compressor
pressure
refrigerant
air conditioner
set value
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JP2008151386A (en
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賢 三浦
武 望月
宏昌 山根
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Toshiba Carrier Corp
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Description

この発明は、圧縮機から吐出される冷媒をガス側渡り配管および液側渡り配管を通して室外ユニットおよび室内ユニットの相互間で循環させる空気調和機に関する。   The present invention relates to an air conditioner that circulates refrigerant discharged from a compressor between an outdoor unit and an indoor unit through a gas side crossover pipe and a liquid side crossover pipe.

従来のＲ２２冷媒に代えて、ＨＦＣ冷媒たとえばＲ４０７Ｃ冷媒やＲ４１０Ａ冷媒を使用する空気調和機がある（例えば特許文献１）。このようなＨＦＣ冷媒を使用する新しい空気調和機に替える場合、部品の再利用や工事費削減の観点から、それまで使用していた空気調和機の既設配管たとえば室外ユニットと室内ユニットとの間のガス側渡り配管および液側渡り配管を、そのまま再利用することが考えられる。
特開２００２―１６２１２６号公報 There is an air conditioner that uses an HFC refrigerant such as R407C refrigerant or R410A refrigerant instead of the conventional R22 refrigerant (for example, Patent Document 1). When switching to such a new air conditioner that uses HFC refrigerant, from the viewpoint of reuse of parts and reduction of construction costs, the existing piping of the air conditioner used so far, for example, between the outdoor unit and the indoor unit is used. It is conceivable to reuse the gas side crossover piping and the liquid side crossover piping as they are.
Japanese Patent Laid-Open No. 2002-162126

しかしながら、Ｒ２２冷媒の代替冷媒であるＨＦＣ冷媒たとえばＲ４１０Ａ冷媒は、同一温度での飽和圧力がＲ２２冷媒やＲ４０７Ｃ冷媒に比べて約１．５倍と高く、再利用される既設配管の設計圧力（耐圧）以上に圧力が上昇してしまう可能性がある。   However, an HFC refrigerant that is an alternative refrigerant of the R22 refrigerant, for example, the R410A refrigerant, has a saturation pressure at the same temperature that is about 1.5 times higher than that of the R22 refrigerant or the R407C refrigerant. ) There is a possibility that the pressure will rise more than that.

この発明は上記の事情を考慮したもので、その目的は、圧力の高い冷媒を使用しながら、しかも既設配管を再利用しながら、圧縮機能力の上昇範囲をできるだけ拡げて運転効率の向上が図れる空気調和機を提供することである。   The present invention takes the above-mentioned circumstances into consideration, and an object of the present invention is to increase the compression function force as much as possible while using a high-pressure refrigerant and reusing existing piping to improve operating efficiency. It is to provide an air conditioner.

請求項１に係る発明の空気調和機は、圧縮機および室外熱交換器を有する室外ユニット、室内熱交換器を有する室内ユニット、これら室外ユニットと室内ユニットとの間に接続されたガス側渡り配管および液側渡り配管を備え、上記圧縮機から吐出される冷媒を上記ガス側渡り配管および上記液側渡り配管を通して上記各ユニット間で循環させるものであって、上記圧縮機から吐出される冷媒の圧力を検知する圧力センサと、この圧力センサの検知圧力が上記各渡り配管の設計圧力に対応する設定値を超過しないよう、上記圧縮機の運転を制御する制御手段と、上記圧縮機の吐出側から上記室外ユニットの冷媒出口までの冷媒の圧力損失を推定する推定手段と、この推定手段で推定される圧力損失の推定値を基に上記設定値を上方に移行する設定値変更手段と、を備えている。そして、上記圧縮機は、空調負荷に応じて回転数が増減される。上記設定値変更手段は、空調負荷に基づく上記圧縮機の単位時間当たりの回転数変化が所定値以上のとき、上記設定値の上方への移行を段階的に行う。 An air conditioner according to a first aspect of the present invention includes an outdoor unit having a compressor and an outdoor heat exchanger, an indoor unit having an indoor heat exchanger, and a gas side crossover pipe connected between the outdoor unit and the indoor unit. The refrigerant discharged from the compressor is circulated between the units through the gas side crossover pipe and the liquid side crossover pipe, and the refrigerant discharged from the compressor A pressure sensor for detecting pressure, control means for controlling the operation of the compressor so that the detected pressure of the pressure sensor does not exceed a set value corresponding to the design pressure of each of the crossover pipes, and a discharge side of the compressor The setting value is shifted upward based on the estimation means for estimating the pressure loss of the refrigerant from the refrigerant outlet to the refrigerant outlet of the outdoor unit, and the estimated value of the pressure loss estimated by the estimation means It is provided with a value change means. And the rotation speed of the said compressor is increased / decreased according to an air-conditioning load. The set value changing means shifts the set value upward in a stepwise manner when the rotation speed change per unit time of the compressor based on the air conditioning load is equal to or greater than a predetermined value.

この発明の空気調和機によれば、圧力の高い冷媒を使用しながら、しかも既設配管を再利用しながら、圧縮機能力の上昇範囲をできるだけ拡げることができる。これにより、運転効率の向上が図れる。   According to the air conditioner of the present invention, the range of increase in the compression function force can be expanded as much as possible while using a high-pressure refrigerant and reusing existing piping. Thereby, the driving efficiency can be improved.

以下、この発明の一実施形態について図面を参照して説明する。図１に冷凍サイクルを示している。
圧縮機１から高圧側配管２にガス冷媒が吐出される。高圧側配管２には、冷媒の逆戻りを防ぐための逆止弁３が設けられている。高圧側配管２に吐出されたガス冷媒は四方弁４およびガス側配管５を通って室外熱交換器６に流れる。室外熱交換器６に流れたガス冷媒は、室外ファン２１から供給される室外空気との熱交換により、凝縮して液冷媒となる。この液冷媒は、液側配管７、室外膨張弁８、リキッドタンク９、および配管接続用の液側パックドバルブ１０を通り、その液側パックドバルブ１０に一端が接続されている液側渡り配管１１に流れる。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a refrigeration cycle.
A gas refrigerant is discharged from the compressor 1 to the high-pressure side pipe 2. The high pressure side pipe 2 is provided with a check valve 3 for preventing the refrigerant from returning backward. The gas refrigerant discharged to the high pressure side pipe 2 flows to the outdoor heat exchanger 6 through the four-way valve 4 and the gas side pipe 5. The gas refrigerant that has flowed to the outdoor heat exchanger 6 is condensed into liquid refrigerant by heat exchange with outdoor air supplied from the outdoor fan 21. The liquid refrigerant passes through the liquid side pipe 7, the outdoor expansion valve 8, the liquid tank 9, and the liquid side packed valve 10 for pipe connection, and the liquid side crossover pipe 11 having one end connected to the liquid side packed valve 10. Flowing into.

液側渡り配管１１に流れた液冷媒は、その液側渡り配管１１の他端が接続されている液側パックドバルブ１２および室内膨張弁１３を通り、室内熱交換器１４に流れる。室内熱交換器１４に流れた液冷媒は、室内ファン２２から供給される室内空気との熱交換により、蒸発してガス冷媒となる。このガス冷媒は、ガス側パックドバルブ１５を通り、そのガス側パックドバルブ１５に一端が接続されているガス側渡り配管１６に流れる。ガス側渡り配管１６に流れたガス冷媒は、そのガス側渡り配管１６の他端が接続されているガス側パックドバルブ１７、ガス側配管１８、上記四方弁４、低圧側配管１９、およびアキュームレータ２０を通り、圧縮機１に吸込まれる。   The liquid refrigerant that has flowed to the liquid side crossover pipe 11 flows to the indoor heat exchanger 14 through the liquid side packed valve 12 and the indoor expansion valve 13 to which the other end of the liquid side crossover pipe 11 is connected. The liquid refrigerant that has flowed to the indoor heat exchanger 14 evaporates into a gas refrigerant by heat exchange with the indoor air supplied from the indoor fan 22. The gas refrigerant flows through the gas side packed valve 15 and flows into the gas side crossover pipe 16 having one end connected to the gas side packed valve 15. The gas refrigerant that has flowed into the gas side crossover pipe 16 is the gas side packed valve 17, the gas side pipe 18, the four-way valve 4, the low pressure side pipe 19, and the accumulator 20 to which the other end of the gas side crossover pipe 16 is connected. And is sucked into the compressor 1.

この冷媒の流れは冷房時のもので、暖房時は四方弁４が切換わることにより、冷媒の流れが反対となって、室内熱交換器１４が凝縮器、室外熱交換器６が蒸発器として機能する。なお、この冷凍サイクルに封入される冷媒として、従来のＲ２２冷媒に代わり、同一温度での飽和圧力が高いＨＦＣ冷媒たとえばＲ４１０Ａ冷媒が使用されている。液側渡り配管１１およびガス側渡り配管１６は、従来のＲ２２冷媒が使用されているときの既設配管であり、再利用されている。   This refrigerant flow is at the time of cooling. When the four-way valve 4 is switched at the time of heating, the refrigerant flow is reversed, so that the indoor heat exchanger 14 is a condenser and the outdoor heat exchanger 6 is an evaporator. Function. As a refrigerant sealed in this refrigeration cycle, an HFC refrigerant having a high saturation pressure at the same temperature, for example, an R410A refrigerant is used instead of the conventional R22 refrigerant. The liquid side crossover piping 11 and the gas side crossover piping 16 are existing piping when a conventional R22 refrigerant is used, and are reused.

上記圧縮機１の吐出側から室外熱交換器６を含む液側パックドバルブ１０までの配管構成、ガス側パックドバルブ１７から圧縮機１の吸込み側までの配管構成、および室外ファン２１などにより、室外ユニットＡが構成されている。また、上記液側パックドバルブ１２から室内熱交換器１４を含むガス側パックドバルブ１５までの配管構成、および室内ファン２２などにより、室内ユニットＢが構成されている。   The piping configuration from the discharge side of the compressor 1 to the liquid side packed valve 10 including the outdoor heat exchanger 6, the piping configuration from the gas side packed valve 17 to the suction side of the compressor 1, the outdoor fan 21, etc. Unit A is configured. An indoor unit B is configured by the piping configuration from the liquid side packed valve 12 to the gas side packed valve 15 including the indoor heat exchanger 14, the indoor fan 22, and the like.

室外ユニットＡにおいて、高圧側配管２に、高圧スイッチＳＷ１、温度センサＴＤ、および圧力センサＰＤが設けられている。高圧スイッチＳＷ１は、圧縮機１から吐出されるガス冷媒の圧力がＲ４１０冷媒に対応した室外ユニットＡの設計圧力よりも上昇した場合に圧縮機１の運転を停止させるためのもので、そのガス冷媒の圧力が上昇して所定値３．７３Ｍｐａ以上になると作動する。温度センサＴＤは、圧縮機１から吐出されるガス冷媒の温度を検知する。圧力センサＰＤは、圧縮機１から吐出されるガス冷媒の圧力を検知する。低圧側配管１９には、温度センサＴＳおよび圧力センサＰＳが設けられている。温度センサＴＳは、圧縮機１に吸込まれるガス冷媒の温度を検知する。圧力センサＰＳは、圧縮機１に吸込まれるガス冷媒の圧力を検知する。   In the outdoor unit A, the high pressure side pipe 2 is provided with a high pressure switch SW1, a temperature sensor TD, and a pressure sensor PD. The high pressure switch SW1 is for stopping the operation of the compressor 1 when the pressure of the gas refrigerant discharged from the compressor 1 rises above the design pressure of the outdoor unit A corresponding to the R410 refrigerant. When the pressure increases to a predetermined value of 3.73 Mpa or more, it operates. The temperature sensor TD detects the temperature of the gas refrigerant discharged from the compressor 1. The pressure sensor PD detects the pressure of the gas refrigerant discharged from the compressor 1. The low pressure side pipe 19 is provided with a temperature sensor TS and a pressure sensor PS. The temperature sensor TS detects the temperature of the gas refrigerant sucked into the compressor 1. The pressure sensor PS detects the pressure of the gas refrigerant sucked into the compressor 1.

また、室外ユニットＡの液側管７において、室外膨張弁８とリキッドタンク９との間に温度センサＴＬが設けられ、液側パックドバルブ１０の近傍（液側渡り配管１１の接続部手前）に高圧スイッチＳＷ２が設けられている。温度センサＴＬは、液冷媒の温度を検知する。高圧スイッチＳＷ２は、室外ユニットＡから液側渡り配管１１に流出する液冷媒の圧力が液側渡り配管１１の設計圧力よりも上昇した場合に圧縮機１の運転を停止させるためのもので、その液冷媒の圧力が上昇して所定値３．３Ｍｐａ以上になると作動する。ガス側管１８には、ガス側パックドバルブ１７の近傍（ガス側渡り配管１６の接続部手前）に高圧スイッチＳＷ３が設けられている。高圧スイッチＳＷ３は、室外ユニットＡからガス側渡り配管１６に流出するガス冷媒（暖房時）の圧力がガス側渡り配管１６の設計圧力よりも上昇した場合に圧縮機１の運転を停止させるためのもので、そのガス冷媒の圧力が上昇して所定値３．３Ｍｐａ以上になると作動する。さらに、室外熱交換器６に熱交換器温度センサＴＥが設けられているとともに、室外ファン２１の吸込み風路に室外温度検知用の室外温度センサＴＯが設けられている。   Further, in the liquid side pipe 7 of the outdoor unit A, a temperature sensor TL is provided between the outdoor expansion valve 8 and the liquid tank 9, and in the vicinity of the liquid side packed valve 10 (before the connection portion of the liquid side transition pipe 11). A high voltage switch SW2 is provided. The temperature sensor TL detects the temperature of the liquid refrigerant. The high pressure switch SW2 is for stopping the operation of the compressor 1 when the pressure of the liquid refrigerant flowing out from the outdoor unit A to the liquid side crossover pipe 11 is higher than the design pressure of the liquid side crossover pipe 11. It operates when the pressure of the liquid refrigerant rises to a predetermined value of 3.3 MPa or more. The gas side pipe 18 is provided with a high pressure switch SW3 in the vicinity of the gas side packed valve 17 (before the connecting portion of the gas side crossover pipe 16). The high pressure switch SW3 is used to stop the operation of the compressor 1 when the pressure of the gas refrigerant (at the time of heating) flowing out from the outdoor unit A to the gas side crossover pipe 16 is higher than the design pressure of the gas side crossover pipe 16. However, it operates when the pressure of the gas refrigerant rises to a predetermined value of 3.3 Mpa or more. Further, the outdoor heat exchanger 6 is provided with a heat exchanger temperature sensor TE, and an outdoor temperature sensor TO for detecting the outdoor temperature is provided in the suction air passage of the outdoor fan 21.

室内ユニットＢでは、室内熱交換器１４に熱交換器温度センサＴＣが設けられ、室内ファン２２の吸込み風路に室内温度検知用の室外温度センサＴＩが設けられている。   In the indoor unit B, the heat exchanger temperature sensor TC is provided in the indoor heat exchanger 14, and the outdoor temperature sensor TI for detecting the indoor temperature is provided in the suction air passage of the indoor fan 22.

そして、これら室外ユニットＡおよび室内ユニットＢを制御するための制御部３０が設けられている。制御部３０は、主要な機能として次の（１）〜（４）を有している。
（１）圧縮機１の回転数Ｎ（rps）（＝運転周波数；圧縮機駆動用インバータの出力周波数）を空調負荷に応じて増減する制御手段。
（２）圧力センサＰＤの検知圧力が各渡り配管１１，１６の設計圧力（耐圧）に対応する設定値Ｐｄｓを超過しないよう、圧縮機１の回転数Ｎを制御する制御手段。 And the control part 30 for controlling the outdoor unit A and the indoor unit B is provided. The control unit 30 has the following (1) to (4) as main functions.
(1) Control means for increasing or decreasing the rotational speed N (rps) of the compressor 1 (= operating frequency; output frequency of the compressor driving inverter) according to the air conditioning load.
(2) Control means for controlling the rotational speed N of the compressor 1 so that the detected pressure of the pressure sensor PD does not exceed the set value Pds corresponding to the design pressure (pressure resistance) of each of the connecting pipes 11 and 16.

（３）圧縮機１の吐出側から室外ユニットＡの冷媒出口までの冷媒の圧力損失ΔＰ０を推定する推定手段。具体的には、圧縮機１の吐出側の冷媒温度Ｔｄ（温度センサＴＤの検知温度）、圧縮機１の吸込側の冷媒温度（飽和蒸発温度；圧力センサＰＳの検知圧力に対応する温度）Ｔｕ、液側渡り配管１１における冷媒温度（温度センサＴＬの検知温度）Ｔｌ、圧縮機１の回転数Ｎなどから、圧力損失の推定値ΔＰ０（kgf/cm2）を算出する。 (3) Estimating means for estimating the pressure loss ΔP0 of the refrigerant from the discharge side of the compressor 1 to the refrigerant outlet of the outdoor unit A. Specifically, the refrigerant temperature Td on the discharge side of the compressor 1 (detected temperature of the temperature sensor TD), the refrigerant temperature on the suction side of the compressor 1 (saturated evaporation temperature; temperature corresponding to the detected pressure of the pressure sensor PS) Tu. Then, an estimated value ΔP0 (kgf / cm 2 ) of the pressure loss is calculated from the refrigerant temperature (detected temperature of the temperature sensor TL) Tl in the liquid side crossover pipe 11, the rotation speed N of the compressor 1, and the like.

（４）上記推定手段で推定される圧力損失ΔＰ０を基に、上記設定値Ｐｄｓを上方に移行（シフトアップ）する設定値変更手段。なお、設定値変更の仕方として、空調負荷に基づく圧縮機１の単位時間当たりの回転数変化ΔＮ（＝Ｎ１−Ｎ０）が所定値ΔＮｘ未満の場合に実行する第１モードと、単位時間当たりの回転数変化ΔＮが所定値ΔＮｘ以上と大きい場合に実行する第２モードとがある。第１モードでは、圧力損失ΔＰ０に制限値ΔＰ１を設け、その制限値ΔＰ１として、ΔＰ０が４．５（kgf/cm2）以上の場合にΔＰ１＝４．５（kgf/cm2）を選定し、ΔＰ０が０．０（kgf/cm2）以下の場合にΔＰ１＝０．０（kgf/cm2）を選定し、ΔＰ０が０．０（kgf/cm2）超かつ４．５（kgf/cm2）未満の場合にΔＰ１＝ΔＰ０を選定する。第２モードでは、圧力損失ΔＰ０に制限値ΔＰ１を設け、その制限値ΔＰ１を圧力損失ΔＰ０へと所定量たとえば毎秒０．０３（kgf/cm2）ずつ段階的に近づける。 (4) Setting value changing means for shifting (shifting up) the setting value Pds upward based on the pressure loss ΔP0 estimated by the estimating means. As a method of changing the set value, the first mode executed when the rotation speed change ΔN (= N 1 −N 0 ) of the compressor 1 based on the air conditioning load is less than a predetermined value ΔNx, and unit time There is a second mode that is executed when the per-rotational speed change ΔN is as large as a predetermined value ΔNx or more. In the first mode, a limit value ΔP1 is provided for the pressure loss ΔP0, and ΔP1 = 4.5 (kgf / cm 2 ) is selected as the limit value ΔP1 when ΔP0 is 4.5 (kgf / cm 2 ) or more. When ΔP0 is 0.0 (kgf / cm 2 ) or less, ΔP1 = 0.0 (kgf / cm 2 ) is selected, and ΔP0 is more than 0.0 (kgf / cm 2 ) and 4.5 (kgf / cm If it is less than cm 2 ), ΔP1 = ΔP0 is selected. In the second mode, a limit value ΔP1 is provided for the pressure loss ΔP0, and the limit value ΔP1 is gradually approached to the pressure loss ΔP0 by a predetermined amount, for example, 0.03 (kgf / cm 2 ) per second.

つぎに、作用を説明する。
まず、圧力損失の推定とそれに関わる制御について、図２のフローチャートを参照しながら説明する。
冷房時（ステップＳ１のＹＥＳ）、圧縮機１の吐出側から室外ユニットＡの冷媒出口（液側パックドバルブ１０）までの冷媒の圧力損失の推定値ΔＰ０が、圧縮機１の吐出側の冷媒温度Ｔｄ（温度センサＴＤの検知温度）、圧縮機１の吸込側の冷媒温度（飽和蒸発温度；圧力センサＰＳの検知圧力に対応する温度）Ｔｕ、液側渡り配管１１における冷媒温度（温度センサＴＬの検知温度）Ｔｌ、圧縮機１の回転数Ｎなどを用いて、下式により算出される（ステップＳ２）。Ｋ１，Ｋ２，Ｋ３，Ｋ４，Ｋ５は、それぞれ定数である。
ΔＰ０＝−Ｋ１−Ｋ２×Ｔｄ＋Ｋ３×Ｔｕ＋Ｋ４×Ｔｌ＋Ｋ５×Ｎ
続いて、空調負荷に基づく圧縮機１の単位時間当たりの回転数変化ΔＮ（＝Ｎ１−Ｎ０）が所定値ΔＮｘ未満であるか否かが判定される（ステップＳ３）。
回転数変化ΔＮが所定値ΔＮｘ未満であれば（ステップＳ３のＹＥＳ）、圧力損失ΔＰ０の制限値ΔＰ１が用意され、その制限値ΔＰ１として、ΔＰ０が４．５（kgf/cm2）以上の場合にΔＰ１＝４．５（kgf/cm2）が選定され、ΔＰ０が０．０（kgf/cm2）以下の場合にΔＰ１＝０．０（kgf/cm2）が選定され、ΔＰ０が０．０（kgf/cm2）超かつ４．５（kgf/cm2）未満の場合にΔＰ１＝ΔＰ０が選定される（ステップＳ４）。 Next, the operation will be described.
First, estimation of pressure loss and control related thereto will be described with reference to the flowchart of FIG.
During cooling (YES in step S1), an estimated value ΔP0 of refrigerant pressure loss from the discharge side of the compressor 1 to the refrigerant outlet (liquid side packed valve 10) of the outdoor unit A is the refrigerant temperature on the discharge side of the compressor 1. Td (temperature detected by the temperature sensor TD), refrigerant temperature on the suction side of the compressor 1 (saturated evaporation temperature; temperature corresponding to the pressure detected by the pressure sensor PS) Tu, refrigerant temperature in the liquid side crossover pipe 11 (of the temperature sensor TL) It is calculated by the following equation using the detected temperature (Tl), the rotational speed N of the compressor 1, and the like (step S2). K 1 , K 2 , K 3 , K 4 , and K 5 are constants.
ΔP0 = −K 1 −K 2 × Td + K 3 × Tu + K 4 × Tl + K 5 × N
Subsequently, it is determined whether or not the rotation speed change ΔN (= N 1 −N 0 ) per unit time of the compressor 1 based on the air conditioning load is less than a predetermined value ΔNx (step S3).
If the rotational speed change ΔN is less than the predetermined value ΔNx (YES in step S3), a limit value ΔP1 of the pressure loss ΔP0 is prepared, and ΔP0 is 4.5 (kgf / cm 2 ) or more as the limit value ΔP1. to ΔP1 = 4.5 (kgf / cm 2 ) is selected, .DELTA.P0 is 0.0 (kgf / cm 2) or less when the ΔP1 = 0.0 (kgf / cm 2 ) is selected, .DELTA.P0 is 0. ΔP1 = ΔP0 is selected when it is greater than 0 (kgf / cm 2 ) and less than 4.5 (kgf / cm 2 ) (step S4).

制限値ΔＰ１が選定されると、その制限値ΔＰ１が圧力スイッチＳＷ２のこれまでの作動回数ｎＡに基づく下式により補正されて、新たな制限値ΔＰ２が求められる（ステップＳ５）。なお、作動回数ｎＡは、４回未満ではｎ回、４回以上で４回が選定され、空気調和機の停止もしくは冷房運転・暖房運転の切換えによりリセットされる。
ΔＰ２＝ΔＰ１−０．５×ｎＡ
そして、新たな制限値ΔＰ２だけ、圧力センサＰＤの検知圧力Ｐｄに対する設定値Ｐｄｓがシフトアップされる（ステップＳ６）。
Ｐｄｓ＝Ｐｄｓ＋ΔＰ２
このシフトアップにより、液冷媒の圧力が液側渡り配管１１の耐圧より十分に低い状態のまま圧縮機１の回転数Ｎが不要に低減されるといった不具合がなくなって、圧縮機能力の上昇範囲が拡がり、運転効率の向上が図れる。すなわち、圧力の高いＲ４１０Ａ冷媒を使用しながら、しかも従来のＲ２２冷媒が使用されているときの既設配管（液側渡り配管１１およびガス側渡り配管１６）を再利用しながら、圧縮機能力の上昇範囲をできるだけ拡げて運転効率の向上が図れる。 When the limit value ΔP1 is selected, the limit value ΔP1 is corrected by the following equation based on the number of times nA of the pressure switch SW2 has been operated so far, and a new limit value ΔP2 is obtained (step S5). The number of actuations nA is selected to be n times, 4 times or more when it is less than 4, and is reset by stopping the air conditioner or switching between cooling operation and heating operation.
ΔP2 = ΔP1-0.5 × nA
Then, the set value Pds with respect to the detected pressure Pd of the pressure sensor PD is shifted up by the new limit value ΔP2 (step S6).
Pds = Pds + ΔP2
This shift up eliminates the problem that the rotational speed N of the compressor 1 is unnecessarily reduced while the pressure of the liquid refrigerant is sufficiently lower than the pressure resistance of the liquid side crossover pipe 11, and the range of increase in the compression function force is increased. It can be expanded and driving efficiency can be improved. That is, while using the R410A refrigerant having a high pressure and reusing the existing pipes (the liquid side crossover pipe 11 and the gas side crossover pipe 16) when the conventional R22 refrigerant is used, the compression function force is increased. The range can be expanded as much as possible to improve operating efficiency.

ステップＳ３の判定において、空調負荷の急激な変動が生じて、圧縮機１の回転数変化が所定値ΔＮｘ以上と大きい場合には（ステップＳ３のＮＯ）、圧力損失ΔＰ０に制限値ΔＰ１が設けられ、その制限値ΔＰ１が圧力損失ΔＰ０へと毎秒０．０３（kgf/cm2）ずつ段階的に近づけられる（ステップＳ７）。 In the determination in step S3, when the air-conditioning load suddenly fluctuates and the change in the rotation speed of the compressor 1 is as large as a predetermined value ΔNx or more (NO in step S3), a limit value ΔP1 is provided for the pressure loss ΔP0. The limit value ΔP1 is gradually approximated to the pressure loss ΔP0 by 0.03 (kgf / cm 2 ) per second (step S7).

この段階的に増加する制限値ΔＰ１が補正されて新たな制限値ΔＰ２が逐次に求められ（ステップＳ５）、その新たな制限値ΔＰ２だけ、圧力センサＰＤの検知圧力Ｐｄに対する設定値Ｐｄｓが逐次にシフトアップされる（ステップＳ６）。
Ｐｄｓ＝Ｐｄｓ＋ΔＰ２
空調負荷の急激な変動によって圧縮機１に大きな回転数変化が生じた場合には、実際の圧力損失と推定圧力損失ΔＰ０とに偏差が生じるため、その推定圧力損失ΔＰ０に対応する分だけ設定値Ｐｄｓが一度にシフトアップされると、その設定値Ｐｄｓに基づく圧縮機１の回転数制御が機能しないまま、圧縮機１から吐出されるガス冷媒の圧力が異常上昇して高圧スイッチＳＷ１が作動してしまう。高圧スイッチＳＷ１が作動すると、圧縮機１が停止してしまう。 The limit value ΔP1 that increases stepwise is corrected, and a new limit value ΔP2 is sequentially obtained (step S5), and the set value Pds for the detected pressure Pd of the pressure sensor PD is sequentially increased by the new limit value ΔP2. Shifting up is performed (step S6).
Pds = Pds + ΔP2
When a large rotational speed change occurs in the compressor 1 due to an abrupt change in the air conditioning load, a deviation occurs between the actual pressure loss and the estimated pressure loss ΔP0. Therefore, a set value corresponding to the estimated pressure loss ΔP0 is set. When Pds is shifted up at once, the pressure of the gas refrigerant discharged from the compressor 1 is abnormally increased and the high-pressure switch SW1 is activated without controlling the rotation speed of the compressor 1 based on the set value Pds. End up. When the high pressure switch SW1 is activated, the compressor 1 is stopped.

しかしながら、上記のように、設定値Ｐｄｓは、逐次に、段階的に、シフトアップされる。この段階的なシフトアップにより、設定値Ｐｄｓに基づく圧縮機１の回転数制御が逐次に繰り返されるようになり、圧縮機１から吐出されるガス冷媒の圧力の不要な異常上昇が防止されて、高圧スイッチＳＷ１の作動が回避される。したがって、圧縮機１の不要な停止を防ぎながら、液冷媒の圧力が液側渡り配管１１の耐圧より十分に低い状態のまま圧縮機１の回転数Ｎが不要に低減されるといった不具合を解消できて、運転効率の向上が図れる。さらに、高圧スイッチＳＷ２を設けたことにより液側渡り配管１１の設計圧力を超えると圧縮機１が停止されるので、安全に設定値Ｐｓｄをシフトアップすることができる。   However, as described above, the set value Pds is shifted up step by step sequentially. By this step-up shift, the rotation speed control of the compressor 1 based on the set value Pds is sequentially repeated, and an unnecessary abnormal increase in the pressure of the gas refrigerant discharged from the compressor 1 is prevented. The operation of the high-pressure switch SW1 is avoided. Therefore, while preventing the compressor 1 from being stopped unnecessarily, it is possible to eliminate the problem that the rotational speed N of the compressor 1 is unnecessarily reduced while the pressure of the liquid refrigerant is sufficiently lower than the pressure resistance of the liquid side crossover pipe 11. Thus, the operation efficiency can be improved. Furthermore, since the compressor 1 is stopped when the design pressure of the liquid side crossover piping 11 is exceeded by providing the high pressure switch SW2, the set value Psd can be safely shifted up.

一方、暖房時（除霜運転や冷媒回収運転を含む）は（ステップＳ１のＮＯ）、圧力損失ΔＰ０の制限値ΔＰ１として“１．０”が選定され（ステップＳ８）、その制限値ΔＰ１が室外ユニットＡの冷媒出口側に位置する圧力スイッチＳＷ３のこれまでの作動回数ｎＢに基づく下式により補正されて、新たな制限値ΔＰ２が求められる（ステップＳ９）。なお、作動回数ｎＢは、６回未満ではｎ回、６回以上で６回が選定され、空気調和機の停止もしくは冷房運転・暖房運転の切換えによりリセットされる。
ΔＰ２＝ΔＰ１−０．５×ｎＢ
そして、新たな制限値ΔＰ２だけ、圧力センサＰＤの検知圧力Ｐｄに対する設定値Ｐｄｓがシフトアップされる（ステップＳ６）。
Ｐｄｓ＝Ｐｄｓ＋ΔＰ２
このシフトアップにより、液冷媒の圧力が液側渡り配管１１の耐圧より十分に低い状態のまま圧縮機１の回転数Ｎが不要に低減されるといった不具合がなくなって、圧縮機能力の上昇範囲が拡がり、運転効率の向上が図れる。さらに、高圧スイッチＳＷ３を設けたことによりガス側渡り配管１６の設計圧力を超えると圧縮機１が停止されるので、安全に設定値Ｐｓｄをシフトアップすることができる。 On the other hand, during heating (including defrosting operation and refrigerant recovery operation) (NO in step S1), “1.0” is selected as the limit value ΔP1 of the pressure loss ΔP0 (step S8), and the limit value ΔP1 is the outdoor value. A new limit value ΔP2 is obtained by correcting the pressure switch SW3 located on the refrigerant outlet side of the unit A according to the following equation based on the number of times of operation nB (step S9). The number of actuations nB is selected to be n times when it is less than 6 or 6 times when it is 6 or more, and is reset by stopping the air conditioner or switching between cooling operation and heating operation.
ΔP2 = ΔP1-0.5 × nB
Then, the set value Pds with respect to the detected pressure Pd of the pressure sensor PD is shifted up by the new limit value ΔP2 (step S6).
Pds = Pds + ΔP2
This shift up eliminates the problem that the rotational speed N of the compressor 1 is unnecessarily reduced while the pressure of the liquid refrigerant is sufficiently lower than the pressure resistance of the liquid side crossover pipe 11, and the range of increase in the compression function force is increased. It can be expanded and driving efficiency can be improved. Furthermore, since the compressor 1 is stopped when the design pressure of the gas side crossover piping 16 is exceeded by providing the high pressure switch SW3, the set value Psd can be safely shifted up.

なお、圧力損失推定式の定数Ｋ１，Ｋ２，Ｋ３，Ｋ４，Ｋ５として“０．４”“０．０３５”“０．１”“０．０１”“０．０３５”が選定された場合の推定値ΔＰ０と、実際に測定される圧力損失との関係を図３に示している。一点鎖線は推定値である。 Note that “0.4”, “0.035”, “0.1”, “0.01”, and “0.035” are selected as the constants K 1 , K 2 , K 3 , K 4 , and K 5 of the pressure loss estimation formula. FIG. 3 shows the relationship between the estimated value ΔP0 in this case and the actually measured pressure loss. A one-dot chain line is an estimated value.

なお、上記実施形態では、１台の圧縮機１を有する冷凍サイクルを例に説明したが、図４に示すように、２台の圧縮機１ａ，１ｂを有する冷凍サイクルの場合にも、同様に実施可能である。２台の圧縮機１ａ，１ｂの採用に伴い、高圧側配管２ａ，２ｂ、逆止弁３ａ，３ｂ、高圧スイッチＳＷ１ａ，ＳＷ１ｂ、温度センサＴＤａ，ＴＤｂが設けられている。この場合、圧力損失推定式の検知温度Ｔｄとして、圧縮機１ａまたは圧縮機１ｂのどちらか１台が運転している場合は、運転中の圧縮機の温度センサＴＤの検知温度Ｔｄを使用し、圧縮機１ａ，１ｂの両方が運転している場合は、温度センサＴＤａ，ＴＤｂの検知温度Ｔｄａ，Ｔｄｂのどちらか高い方の値が使用される。   In the above embodiment, the refrigeration cycle having one compressor 1 has been described as an example. However, as shown in FIG. 4, the same applies to a refrigeration cycle having two compressors 1a and 1b. It can be implemented. With the adoption of the two compressors 1a and 1b, high-pressure side pipes 2a and 2b, check valves 3a and 3b, high-pressure switches SW1a and SW1b, and temperature sensors TDa and TDb are provided. In this case, when one of the compressor 1a or the compressor 1b is operating as the detected temperature Td of the pressure loss estimation formula, the detected temperature Td of the temperature sensor TD of the operating compressor is used, When both the compressors 1a and 1b are operating, the higher value of the detected temperatures Tda and Tdb of the temperature sensors TDa and TDb is used.

圧力損失推定式の圧縮機回転数Ｎとして、圧縮機１ａまたは圧縮機１ｂのどちらか１台が運転している場合は、運転中の圧縮機の回転数を使用し、圧縮機１ａ，１ｂの両方が運転している場合は、各圧縮機の回転数を合計した値が使用される。   When either one of the compressor 1a or the compressor 1b is operating as the compressor rotational speed N of the pressure loss estimation formula, the rotational speed of the operating compressor is used, and the compressor 1a, 1b When both are operating, the total number of rotations of each compressor is used.

高圧スイッチＳＷ１ａが作動した場合は圧縮機１ａが停止し、高圧スイッチＳＷ１ｂが作動した場合は圧縮機１ｂが停止し、高圧スイッチＳＷ２，ＳＷ３のどちらか一方が作動すると圧縮機１ａ，１ｂの両方が停止するようになっている。   When the high pressure switch SW1a is operated, the compressor 1a is stopped. When the high pressure switch SW1b is operated, the compressor 1b is stopped. When one of the high pressure switches SW2 and SW3 is operated, both the compressors 1a and 1b are turned on. It comes to stop.

これにより、２台の圧縮機１ａ，１ｂを有する冷凍サイクルの場合にも、渡り配管１１，１６の設計圧力より十分に低い状態のまま圧縮機１ａ，１ｂの回転数Ｎが不要に低減されるといった不具合がなくなって、圧縮機能力の上昇範囲が拡がり、運転効率の向上が図れる。さらに、高圧スイッチＳＷ２，ＳＷ３を設けたことにより渡り配管１１，１６の設計圧力を超えると圧縮機１ａ，１ｂの両方が停止されるので、安全に設定値Ｐｓｄをシフトアップすることができる。   Thereby, also in the case of a refrigeration cycle having two compressors 1a and 1b, the rotational speed N of the compressors 1a and 1b is unnecessarily reduced while being sufficiently lower than the design pressure of the transition pipes 11 and 16. Thus, the range of increase in the compression function force is expanded, and the driving efficiency can be improved. Furthermore, since both the compressors 1a and 1b are stopped when the design pressure of the transition pipes 11 and 16 is exceeded by providing the high pressure switches SW2 and SW3, the set value Psd can be safely shifted up.

その他、この発明は上記実施形態に限定されるものではなく、要旨を変えない範囲で種々変形実施可能である。   In addition, the present invention is not limited to the above embodiment, and various modifications can be made without departing from the scope of the invention.

一実施形態の冷凍サイクルの構成を示す図。The figure which shows the structure of the refrigerating cycle of one Embodiment. 一実施形態の圧力損失の推定とそれに関わる制御を説明するためのフローチャート。The flowchart for demonstrating the estimation of the pressure loss of one Embodiment, and the control in connection with it. 一実施形態の推定値と実際値との関係を示す図。The figure which shows the relationship between the estimated value of one Embodiment, and an actual value. 一実施形態の冷凍サイクルの変形例の構成を示す図。The figure which shows the structure of the modification of the refrigerating cycle of one Embodiment.

符号の説明Explanation of symbols

Ａ…室外ユニット、Ｂ…室内ユニット、１…圧縮機、２…高圧側配管、４…四方弁、６…室外熱交換器、７…液側配管、８…室外膨張弁、９…リキッドタンク、１０…液側パックドバルブ、１１…液側渡り配管、１２…液側パックドバルブ、１３…室内膨張弁、１４…室内熱交換器、１５…ガス側パックドバルブ、１６…ガス側渡り配管、１７…ガス側パックドバルブ、１８…ガス側配管、１９…低圧側配管、２０…アキュームレータ、ＳＷ１，ＳＷ２，ＳＷ３…高圧スイッチ、ＴＤ，ＴＬ，ＴＳ…温度センサ、ＰＤ，ＰＳ…圧力センサ、ＴＥ，ＴＣ…熱交換器温度センサ、ＴＯ…室外温度センサ、ＴＩ…室内温度センサ、３０…制御部   A ... outdoor unit, B ... indoor unit, 1 ... compressor, 2 ... high pressure side piping, 4 ... four-way valve, 6 ... outdoor heat exchanger, 7 ... liquid side piping, 8 ... outdoor expansion valve, 9 ... liquid tank, DESCRIPTION OF SYMBOLS 10 ... Liquid side packed valve, 11 ... Liquid side crossover piping, 12 ... Liquid side packed valve, 13 ... Indoor expansion valve, 14 ... Indoor heat exchanger, 15 ... Gas side packed valve, 16 ... Gas side crossover piping, 17 ... Gas side packed valve, 18 ... gas side piping, 19 ... low pressure side piping, 20 ... accumulator, SW1, SW2, SW3 ... high pressure switch, TD, TL, TS ... temperature sensor, PD, PS ... pressure sensor, TE, TC ... Heat exchanger temperature sensor, TO ... outdoor temperature sensor, TI ... indoor temperature sensor, 30 ... control unit

Claims (3)

圧縮機および室外熱交換器を有する室外ユニット、室内熱交換器を有する室内ユニット、これら室外ユニットと室内ユニットとの間に接続されたガス側渡り配管および液側渡り配管を備え、前記圧縮機から吐出される冷媒を前記ガス側渡り配管および前記液側渡り配管を通して前記各ユニット間で循環させる空気調和機において、
前記圧縮機から吐出される冷媒の圧力を検知する圧力センサと、
前記圧力センサの検知圧力が前記各渡り配管の設計圧力に対応する設定値を超過しないよう、前記圧縮機の運転を制御する制御手段と、
前記圧縮機の吐出側から前記室外ユニットの冷媒出口までの冷媒の圧力損失を推定する推定手段と、
前記推定手段で推定される圧力損失の推定値を基に前記設定値を上方に移行する設定値変更手段と、
を備え、
前記圧縮機は、空調負荷に応じて回転数が増減され、
前記設定値変更手段は、空調負荷に基づく前記圧縮機の単位時間当たりの回転数変化が所定値以上のとき、前記設定値の上方への移行を段階的に行う、
ことを特徴とする空気調和機。 An outdoor unit having a compressor and an outdoor heat exchanger, an indoor unit having an indoor heat exchanger, a gas side crossover pipe and a liquid side crossover pipe connected between the outdoor unit and the indoor unit, from the compressor In the air conditioner for circulating the discharged refrigerant between the units through the gas side crossover pipe and the liquid side crossover pipe,
A pressure sensor for detecting the pressure of the refrigerant discharged from the compressor;
Control means for controlling the operation of the compressor so that the detected pressure of the pressure sensor does not exceed a set value corresponding to the design pressure of each of the connecting pipes;
Estimating means for estimating a pressure loss of refrigerant from a discharge side of the compressor to a refrigerant outlet of the outdoor unit;
A set value changing means for moving the set value upward based on an estimated value of pressure loss estimated by the estimating means;
Equipped with a,
The number of rotations of the compressor is increased or decreased according to the air conditioning load,
The set value changing means performs the upward transition of the set value in a stepwise manner when the rotational speed change per unit time of the compressor based on the air conditioning load is a predetermined value or more.
An air conditioner characterized by that. 前記推定手段は、前記圧縮機の吐出側の冷媒温度、前記圧縮機の吸込側の冷媒温度、前記液側渡り配管における冷媒温度、前記圧縮機の回転数から、前記圧力損失の推定値を算出する、
ことを特徴とする請求項１に記載の空気調和機。 The estimation means calculates the estimated value of the pressure loss from the refrigerant temperature on the discharge side of the compressor, the refrigerant temperature on the suction side of the compressor, the refrigerant temperature in the liquid side crossover piping, and the rotation speed of the compressor. To
The air conditioner according to claim 1. 前記室外ユニットは、所定値以上の圧力を検知すると前記圧縮機の運転を停止させるための複数の高圧スイッチを有し、これら高圧スイッチは前記圧縮機の冷媒吐出側および前記各渡り配管の接続部手前にそれぞれ設けられていることを特徴とする請求項１または請求項２に記載の空気調和機。 The outdoor unit has a plurality of high-pressure switches for stopping the operation of the compressor when a pressure equal to or higher than a predetermined value is detected, and the high-pressure switches are connected to the refrigerant discharge side of the compressor and the connecting portions of the crossover pipes. The air conditioner according to claim 1 , wherein the air conditioner is provided in front of the air conditioner.
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