JP2006258381A - Air conditioner - Google Patents

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JP2006258381A
JP2006258381A JP2005077264A JP2005077264A JP2006258381A JP 2006258381 A JP2006258381 A JP 2006258381A JP 2005077264 A JP2005077264 A JP 2005077264A JP 2005077264 A JP2005077264 A JP 2005077264A JP 2006258381 A JP2006258381 A JP 2006258381A
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expansion valve
heat exchanger
air conditioner
refrigerant
compressor
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JP4550635B2 (en
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Toshiaki Takano
利明 高野
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Sharp Corp
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Sharp Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

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Abstract

<P>PROBLEM TO BE SOLVED: To provide an air conditioner capable of preventing generation of abnormal sound of an expansion valve. <P>SOLUTION: In this air conditioner, an entrance temperature T1 and an exit temperature T2 of the expansion valve 6 are detected by thermistors 7 and 8, respectively; and, when the difference T1-T2 between them is above a predetermined value TR, the driving frequency of a compressor 5 is lowered by a predetermined frequency Δf. Thereby, the difference between the pressure at the entrance of the expansion valve 6 and that of the exit thereof can be adjusted to not greater than a predetermined value, and the generation of the abnormal sound of the expansion valve 6 can be prevented. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

この発明は空気調和機に関し、特に、室外熱交換器と室内熱交換器と圧縮機と膨張弁とを備えた空気調和機に関する。   The present invention relates to an air conditioner, and more particularly to an air conditioner including an outdoor heat exchanger, an indoor heat exchanger, a compressor, and an expansion valve.

従来より、空気調和機には、室外熱交換器と室内熱交換器と圧縮機と膨張弁とが設けられている。冷房時は、圧縮機で圧縮された冷媒が室外熱交換器で液化され、液化された冷媒が膨張弁で減圧され、減圧された冷媒が室内熱交換器で蒸発し、蒸発した冷媒が圧縮機に戻される。暖房時は、圧縮機で圧縮された冷媒が室内熱交換器で液化され、液化された冷媒が膨張弁で減圧され、減圧された冷媒が室外熱交換器で蒸発し、蒸発した冷媒が圧縮機に戻される（たとえば特許文献１参照）。
特開２００４−３７１７号公報 Conventionally, an air conditioner is provided with an outdoor heat exchanger, an indoor heat exchanger, a compressor, and an expansion valve. During cooling, the refrigerant compressed by the compressor is liquefied by the outdoor heat exchanger, the liquefied refrigerant is decompressed by the expansion valve, the decompressed refrigerant is evaporated by the indoor heat exchanger, and the evaporated refrigerant is the compressor. Returned to During heating, the refrigerant compressed by the compressor is liquefied by the indoor heat exchanger, the liquefied refrigerant is decompressed by the expansion valve, the decompressed refrigerant is evaporated by the outdoor heat exchanger, and the evaporated refrigerant is the compressor. (For example, refer to Patent Document 1).
JP 2004-3717 A

しかし、従来の空気調和機では、膨張弁の入口と出口の間の圧力差が大きくなると、冷媒の流量制御が困難になり、異常音が発生するという問題があった。この問題は、膨張弁の下側開口部から横側開口部に冷媒が流れる暖房時で特に顕著であった。   However, the conventional air conditioner has a problem that when the pressure difference between the inlet and outlet of the expansion valve becomes large, it becomes difficult to control the flow rate of the refrigerant and abnormal noise is generated. This problem was particularly noticeable during heating when the refrigerant flows from the lower opening of the expansion valve to the lateral opening.

それゆえに、この発明の主たる目的は、膨張弁の異常音の発生を防止することが可能な空気調和機を提供することである。   Therefore, a main object of the present invention is to provide an air conditioner that can prevent the occurrence of abnormal noise of an expansion valve.

この発明に係る空気調和機は、各々が空気と冷媒の熱交換を行なう第１および第２の熱交換器と、それぞれ第１および第２の熱交換器に空気を送る第１および第２の送風機と、第１の熱交換器で蒸発した冷媒を圧縮して第２の熱交換器に与える圧縮機と、第２の熱交換器で液化された冷媒を減圧して第１の熱交換器に与える膨張弁と、膨張弁の入口と出口の圧力差を検出する検出手段と、検出手段によって検出された圧力差が予め定められた値を超えたことに応じて圧縮機の駆動周波数を低下させる制御手段とを備えたものである。したがって、膨張弁の入口と出口の圧力差を所定値以下に調整することができ、膨張弁の異常音の発生を防止することができる。   The air conditioner according to the present invention includes first and second heat exchangers each for exchanging heat between air and refrigerant, and first and second air for sending air to the first and second heat exchangers, respectively. A blower, a compressor that compresses the refrigerant evaporated by the first heat exchanger and applies it to the second heat exchanger, and a first heat exchanger that decompresses the refrigerant liquefied by the second heat exchanger. An expansion valve, a detection means for detecting the pressure difference between the inlet and the outlet of the expansion valve, and the compressor drive frequency is lowered when the pressure difference detected by the detection means exceeds a predetermined value. And a control means for making it. Therefore, the pressure difference between the inlet and outlet of the expansion valve can be adjusted to a predetermined value or less, and abnormal noise of the expansion valve can be prevented.

好ましくは、検出手段は、膨張弁の入口と出口の温度差を検出し、制御手段は、検出手段によって検出された温度差が予め定められた温度差を超えた場合に膨張弁の入口と出口の圧力差が予め定められた値を超えたと判断する。この場合は、圧力差を容易にモニタすることができる。   Preferably, the detection means detects a temperature difference between the inlet and outlet of the expansion valve, and the control means detects that the temperature difference detected by the detection means exceeds a predetermined temperature difference. Is determined to have exceeded a predetermined value. In this case, the pressure difference can be easily monitored.

また好ましくは、制御手段は、検出手段によって検出された圧力差が予め定められた値を超えている場合は、圧縮機の駆動周波数を所定時間毎に所定周波数ずつ低下させる。この場合は、より確実に圧力差を小さくすることができる。   Further preferably, when the pressure difference detected by the detecting means exceeds a predetermined value, the control means decreases the driving frequency of the compressor by a predetermined frequency every predetermined time. In this case, the pressure difference can be reduced more reliably.

また好ましくは、制御手段は、検出手段によって検出された圧力差が予め定められた値を超えたことに応じて、圧縮機の駆動周波数を低下させるとともに、第１の送風機の送風能力を低下させる。この場合は、より確実に圧力差を小さくすることができる。   Preferably, the control means lowers the driving frequency of the compressor and lowers the blowing capacity of the first blower in response to the pressure difference detected by the detection means exceeding a predetermined value. . In this case, the pressure difference can be reduced more reliably.

また好ましくは、膨張弁は、弁座と、該弁座の中心線に沿って移動可能に設けられた弁棒とを含み、膨張弁の入口は、弁棒の長さ方向に設けられ、膨張弁の出口は、弁棒の長さ方向と直交する方向に設けられている。本願発明は、この場合に特に有効である。   Preferably, the expansion valve includes a valve seat and a valve rod provided so as to be movable along the center line of the valve seat, and an inlet of the expansion valve is provided in a length direction of the valve rod, The outlet of the valve is provided in a direction orthogonal to the length direction of the valve stem. The present invention is particularly effective in this case.

また好ましくは、第１の熱交換器は室外に設けられ、第２の熱交換器は室内に設けられている。   Preferably, the first heat exchanger is provided outdoors and the second heat exchanger is provided indoors.

以上のように、この発明によれば、膨張弁の入口と出口の間の圧力差を所定値以下に調整するので、冷媒の流量制御が困難になったり、異常音が発生することがない。   As described above, according to the present invention, the pressure difference between the inlet and the outlet of the expansion valve is adjusted to a predetermined value or less, so that it becomes difficult to control the flow rate of the refrigerant and no abnormal noise is generated.

図１は、この発明の一実施の形態による空気調和機の冷房／暖房サイクルを示す図である。図１において、この空気調和機は、室外ユニット１と室内ユニット１０を備える。   FIG. 1 is a diagram showing a cooling / heating cycle of an air conditioner according to an embodiment of the present invention. In FIG. 1, the air conditioner includes an outdoor unit 1 and an indoor unit 10.

室外ユニット１は、室外熱交換器２、室外送風機３、四方弁４、圧縮機５、膨張弁６、およびサーミスタ７，８を含み、室内ユニット１０は室内熱交換器１１および室内送風機１２を含む。室外熱交換器２は、冷媒と室外空気の熱交換を行なう。室外送風機３は、室外熱交換器２に室外空気を供給する。四方弁４は、冷房時は圧縮機５の吸込口５ａおよび吐出口５ｂをそれぞれ室内熱交換器１１および室外熱交換器２に接続し、暖房時は圧縮機５の吸込口５ａおよび吐出口５ｂをそれぞれ室外熱交換器２および室内熱交換器１１に接続する。圧縮機５は、蒸発した冷媒を圧縮する。膨張弁６は、液化した冷媒を減圧する。   The outdoor unit 1 includes an outdoor heat exchanger 2, an outdoor fan 3, a four-way valve 4, a compressor 5, an expansion valve 6, and the thermistors 7 and 8, and the indoor unit 10 includes an indoor heat exchanger 11 and an indoor fan 12. . The outdoor heat exchanger 2 performs heat exchange between the refrigerant and the outdoor air. The outdoor blower 3 supplies outdoor air to the outdoor heat exchanger 2. The four-way valve 4 connects the suction port 5a and the discharge port 5b of the compressor 5 to the indoor heat exchanger 11 and the outdoor heat exchanger 2 respectively during cooling, and the suction port 5a and the discharge port 5b of the compressor 5 during heating. Are connected to the outdoor heat exchanger 2 and the indoor heat exchanger 11, respectively. The compressor 5 compresses the evaporated refrigerant. The expansion valve 6 depressurizes the liquefied refrigerant.

図２は、図１に示した膨張弁６の構成を示す断面図である。図２において、膨張弁６は弁本体２０を含む。弁本体２０の内部には、リング状の弁座２１が形成され、弁座２１の中心線に沿って弁棒２２が配置されている。弁棒２２の下端は円錐状に形成されており、弁棒２２は弁座２１に対して近づきまたは離れる方向すなわち図中上下方向に移動可能に設けられている。弁本体２０の横側開口部には横銅管２３が接合され、弁本体２０の下側開口部には下銅管２４が接合されている。横銅管２３は室外熱交換器２に接続され、下銅管２４は室内熱交換器１１に接続される。   FIG. 2 is a cross-sectional view showing the configuration of the expansion valve 6 shown in FIG. In FIG. 2, the expansion valve 6 includes a valve body 20. A ring-shaped valve seat 21 is formed inside the valve body 20, and a valve rod 22 is disposed along the center line of the valve seat 21. The lower end of the valve stem 22 is formed in a conical shape, and the valve stem 22 is provided so as to be movable toward or away from the valve seat 21, that is, up and down in the drawing. A lateral copper tube 23 is joined to the lateral opening of the valve body 20, and a lower copper tube 24 is joined to the lower opening of the valve body 20. The horizontal copper pipe 23 is connected to the outdoor heat exchanger 2, and the lower copper pipe 24 is connected to the indoor heat exchanger 11.

また、弁本体２０の上部には、弁棒２２を上下動させるためのステッピングモータ２５が設けられている。ステッピングモータ２５のロータ２６は弁棒２２の上端部に結合されている。弁本体２０の上部外周部にはネジ溝が形成されており、ロータ２６の内周部はそのネジ溝に螺合されている。ステッピングモータ２５のステータ２７の電磁コイル２８に正パルスを与えるとロータ２６が正方向に所定角度だけ回転して弁棒２２が所定距離だけ弁座２１に近づく。電磁コイル２８に負パルスを与えるとロータ２６が負方向に所定角度だけ回転して弁棒２２が所定距離だけ弁座２１から離れる。弁棒２２を上下動させることにより、弁棒２２の先端部と弁座２１の隙間面積を変化させて、そこを通過する冷媒の流量を調節することができる。   Further, a stepping motor 25 for moving the valve rod 22 up and down is provided on the upper part of the valve body 20. The rotor 26 of the stepping motor 25 is coupled to the upper end portion of the valve rod 22. A screw groove is formed in the upper outer peripheral portion of the valve body 20, and the inner peripheral portion of the rotor 26 is screwed into the screw groove. When a positive pulse is applied to the electromagnetic coil 28 of the stator 27 of the stepping motor 25, the rotor 26 rotates by a predetermined angle in the positive direction and the valve rod 22 approaches the valve seat 21 by a predetermined distance. When a negative pulse is applied to the electromagnetic coil 28, the rotor 26 rotates by a predetermined angle in the negative direction, and the valve rod 22 moves away from the valve seat 21 by a predetermined distance. By moving the valve rod 22 up and down, the gap area between the tip of the valve rod 22 and the valve seat 21 can be changed, and the flow rate of the refrigerant passing therethrough can be adjusted.

この膨張弁６は、冷房時は、室外熱交換器２から横銅管２３を介して与えられる冷媒を減圧して下銅管２４を介して室内熱交換器１１に与え、暖房時は、室内熱交換器１１から下銅管２４を介して与えられる冷媒を減圧して横銅管２３を介して室外熱交換器２に与える。この膨張弁６では、下側開口部に供給される冷媒と上側開口部から吐出される冷媒との圧力差が所定値以上になると冷媒の流量制御が困難になり、異常音が発生する。   The expansion valve 6 depressurizes the refrigerant supplied from the outdoor heat exchanger 2 via the horizontal copper pipe 23 during cooling, and applies the reduced pressure to the indoor heat exchanger 11 via the lower copper pipe 24. The refrigerant supplied from the heat exchanger 11 through the lower copper pipe 24 is depressurized and supplied to the outdoor heat exchanger 2 through the horizontal copper pipe 23. In the expansion valve 6, if the pressure difference between the refrigerant supplied to the lower opening and the refrigerant discharged from the upper opening becomes a predetermined value or more, it becomes difficult to control the flow rate of the refrigerant, and abnormal noise is generated.

図１に戻って、サーミスタ７は、膨張弁６の下銅管２４の温度Ｔ１を検出し、検出値を示す信号を出力する。サーミスタ８は、膨張弁６の横銅管２３の温度Ｔ２を検出し、検出値を示す信号を出力する。サーミスタ７，８の検出温度Ｔ１，Ｔ２の差は、暖房時における膨張弁６の入口と出口の圧力差と相関があるので、サーミスタ７，８の検出温度Ｔ１，Ｔ２の差をモニタすることにより暖房時における膨張弁６の入口と出口の圧力差を簡単な構成でモニタすることができる。室内熱交換器１１は、冷媒と室内空気の熱交換を行なう。室外送風機１２は、室内熱交換器１１に室外空気を供給する。   Returning to FIG. 1, the thermistor 7 detects the temperature T1 of the lower copper tube 24 of the expansion valve 6 and outputs a signal indicating the detected value. The thermistor 8 detects the temperature T2 of the copper pipe 23 of the expansion valve 6 and outputs a signal indicating the detected value. Since the difference between the detected temperatures T1 and T2 of the thermistors 7 and 8 is correlated with the pressure difference between the inlet and outlet of the expansion valve 6 during heating, the difference between the detected temperatures T1 and T2 of the thermistors 7 and 8 is monitored. The pressure difference between the inlet and the outlet of the expansion valve 6 during heating can be monitored with a simple configuration. The indoor heat exchanger 11 performs heat exchange between the refrigerant and the room air. The outdoor blower 12 supplies outdoor air to the indoor heat exchanger 11.

図３は、この空気調和機の電気回路図である。図３において、この空気調和機は、制御部３０、スイッチ３１〜３３およびインバータ３４を含む。室外送風機３とスイッチ３１、室外送風機１２とスイッチ３２、四方弁４とスイッチ３３は、それぞれ電源端子間に直列接続されている。スイッチ３１，３２がオンされると、それぞれ室外送風機３および室外送風機１２に電源電圧が供給される。スイッチ３３がオンされるかオフされるかにより四方弁４の接続状態の切換えが行なわれる。インバータ３５は、制御部３０の指示に応じた周波数の交流電圧を圧縮機５に与える。   FIG. 3 is an electric circuit diagram of the air conditioner. In FIG. 3, the air conditioner includes a control unit 30, switches 31 to 33, and an inverter 34. The outdoor fan 3 and the switch 31, the outdoor fan 12 and the switch 32, and the four-way valve 4 and the switch 33 are respectively connected in series between the power supply terminals. When the switches 31 and 32 are turned on, the power supply voltage is supplied to the outdoor fan 3 and the outdoor fan 12, respectively. The connection state of the four-way valve 4 is switched depending on whether the switch 33 is turned on or off. The inverter 35 supplies an AC voltage having a frequency according to an instruction from the control unit 30 to the compressor 5.

制御部３０は、操作部(図示せず)からの信号（冷房／暖房の切換を指示する信号、駆動の開始／停止を指示する信号、冷房能力のレベルを指示する信号、暖房能力のレベルを指示する信号など）とサーミスタ７，８の出力信号とに基づいて、スイッチ３１〜３３のオン／オフ制御、室外送風機３の送風量の制御、室内送風機１２の送風量の制御、四方弁４の切換制御、膨張弁６の開度の制御、インバータ３５の出力電圧の周波数の制御などを行なう。   The control unit 30 receives signals from an operation unit (not shown) (a signal for instructing switching between cooling / heating, a signal for instructing start / stop of driving, a signal for instructing the level of cooling capacity, and a level of heating capacity) Based on the output signals of the thermistors 7 and 8, on / off control of the switches 31 to 33, control of the air volume of the outdoor fan 3, control of the air volume of the indoor fan 12, and the four-way valve 4 Switching control, control of the opening degree of the expansion valve 6, control of the frequency of the output voltage of the inverter 35, and the like are performed.

特に、制御部３０は、暖房時にサーミスタ７，８の検出温度Ｔ１，Ｔ２の差Ｔ１−Ｔ２が所定温度ＴＲ以上である場合は、圧縮機５の駆動周波数を所定周波数Δｆだけ下げる。これにより、膨張弁６に供給される冷媒の圧力を下げて膨張弁６の入口と出口の圧力差を下げることができる。   In particular, when the difference T1-T2 between the detected temperatures T1 and T2 of the thermistors 7 and 8 is equal to or higher than the predetermined temperature TR during heating, the control unit 30 decreases the drive frequency of the compressor 5 by the predetermined frequency Δf. Thereby, the pressure of the refrigerant supplied to the expansion valve 6 can be lowered, and the pressure difference between the inlet and the outlet of the expansion valve 6 can be lowered.

次に、この空気調和機の動作について説明する。ユーザによって冷房運転の開始が指示されると、スイッチ３１〜３３がオンされて室外送風機３および室内送風機１２が駆動されるとともに、四方弁４によって圧縮機５の吸込口５ａおよび吐出口５ｂがそれぞれ室内熱交換器１１および室外熱交換器２に接続される。また、膨張弁６の開度が所定値に設定され、圧縮機５の運転が開始される。   Next, the operation of this air conditioner will be described. When the start of the cooling operation is instructed by the user, the switches 31 to 33 are turned on to drive the outdoor blower 3 and the indoor blower 12, and the suction port 5 a and the discharge port 5 b of the compressor 5 are respectively set by the four-way valve 4. Connected to the indoor heat exchanger 11 and the outdoor heat exchanger 2. Moreover, the opening degree of the expansion valve 6 is set to a predetermined value, and the operation of the compressor 5 is started.

圧縮機５で圧縮された冷媒ガスは室外熱交換器２に送られる。この冷媒ガスは、室外熱交換器２で室外空気と熱交換し、凝縮液化する。この凝縮液は膨張弁６で減圧され、室内熱交換器１１内で蒸発して気化熱を奪い、室内熱交換器１１を冷却させる。室内空気は、室内送風機１２によって室内熱交換器１１に送られて冷却および除湿される。蒸発した冷媒ガスは圧縮機５に戻り、冷房サイクルが繰り返される。   The refrigerant gas compressed by the compressor 5 is sent to the outdoor heat exchanger 2. This refrigerant gas exchanges heat with outdoor air in the outdoor heat exchanger 2 and is condensed and liquefied. This condensate is depressurized by the expansion valve 6, evaporates in the indoor heat exchanger 11, takes heat of vaporization, and cools the indoor heat exchanger 11. The indoor air is sent to the indoor heat exchanger 11 by the indoor blower 12 to be cooled and dehumidified. The evaporated refrigerant gas returns to the compressor 5 and the cooling cycle is repeated.

また、ユーザによって暖房運転の開始が指示されると、スイッチ３１，３２がオンされるとともにスイッチ３３がオフされ、室外送風機３および室内送風機１２が駆動されるとともに、四方弁４によって圧縮機５の吸込口５ａおよび吐出口５ｂがそれぞれ室外熱交換器２および室内熱交換器１１に接続される。また、膨張弁６の開度が所定値に設定され、圧縮機５の運転が開始される。   When the user instructs the start of the heating operation, the switches 31 and 32 are turned on, the switch 33 is turned off, the outdoor blower 3 and the indoor blower 12 are driven, and the compressor 5 is driven by the four-way valve 4. The suction port 5a and the discharge port 5b are connected to the outdoor heat exchanger 2 and the indoor heat exchanger 11, respectively. Moreover, the opening degree of the expansion valve 6 is set to a predetermined value, and the operation of the compressor 5 is started.

圧縮機５で圧縮された冷媒ガスは室内熱交換器１１に送られる。この冷媒ガスは、室内熱交換器１１で室内空気と熱交換し、凝縮液化する。冷媒の凝縮熱によって室内空気が加熱される。冷媒の凝縮液は膨張弁６で減圧され、室外熱交換器２内で蒸発する。蒸発した冷媒ガスは圧縮機５に戻り、暖房サイクルが繰り返される。   The refrigerant gas compressed by the compressor 5 is sent to the indoor heat exchanger 11. This refrigerant gas exchanges heat with indoor air in the indoor heat exchanger 11 to be condensed and liquefied. The room air is heated by the heat of condensation of the refrigerant. The refrigerant condensate is decompressed by the expansion valve 6 and evaporated in the outdoor heat exchanger 2. The evaporated refrigerant gas returns to the compressor 5 and the heating cycle is repeated.

暖房時に膨張弁６の入口と出口の圧力差が所定値以上になると、膨張弁６において冷媒の流量調整が不能になり、異常音が発生する。このような状態は、たとえば気温が比較的高いのに暖房能力が高く設定され、室外熱交換器２で冷媒の蒸発が促進されるとともに圧縮機５の駆動周波数が高められた場合に発生する。本願発明では、このような場合は圧縮機５の駆動周波数を強制的に低下させる。   If the pressure difference between the inlet and the outlet of the expansion valve 6 becomes a predetermined value or more during heating, the refrigerant flow rate adjustment in the expansion valve 6 becomes impossible and abnormal noise is generated. Such a state occurs, for example, when the heating capacity is set high even when the air temperature is relatively high, evaporation of the refrigerant is promoted in the outdoor heat exchanger 2 and the driving frequency of the compressor 5 is increased. In the present invention, in such a case, the driving frequency of the compressor 5 is forcibly reduced.

すなわち図４に示すように、ステップＳ１において所定時間が経過するのを待ち、ステップＳ２においてサーミスタ７，８によって膨張弁６の入口温度Ｔ１と出口温度Ｔ２を検出する。ステップＳ３において膨張弁６の入口温度Ｔ１と出口温度Ｔ２の差Ｔ１−Ｔ２が所定温度ＴＲ以上であるか否かを判別し、Ｔ１−Ｔ２≧ＴＲでない場合はステップＳ１に戻り、Ｔ１−Ｔ２≧ＴＲである場合はステップＳ４において圧縮機５の駆動周波数を所定周波数Δｆだけ低下させる。これにより、所定時間毎に圧縮機５の吐出ガスの圧力を下げて膨張弁６の入口と出口の圧力差を上げることができ、膨張弁６の異常音の発生を防止することができる。   That is, as shown in FIG. 4, after waiting for a predetermined time in step S1, the thermistors 7 and 8 detect the inlet temperature T1 and the outlet temperature T2 of the expansion valve 6 in step S2. In step S3, it is determined whether or not the difference T1-T2 between the inlet temperature T1 and the outlet temperature T2 of the expansion valve 6 is equal to or higher than a predetermined temperature TR. If T1-T2 ≧ TR, the process returns to step S1, and T1-T2 ≧ If it is TR, the drive frequency of the compressor 5 is lowered by a predetermined frequency Δf in step S4. Thereby, the pressure of the discharge gas of the compressor 5 can be lowered every predetermined time to increase the pressure difference between the inlet and the outlet of the expansion valve 6, and the occurrence of abnormal noise of the expansion valve 6 can be prevented.

なお、ステップＳ４において圧縮機５の駆動周波数を所定周波数Δｆだけ低下させとともに、室外送風機３の送風量を所定量だけ低下させてもよい。この場合は、室外熱交換器２における冷媒の蒸発を抑制することができ、圧縮機５の吐出ガスの圧力を一層下げることができる。   In step S4, the drive frequency of the compressor 5 may be decreased by a predetermined frequency Δf, and the air flow rate of the outdoor blower 3 may be decreased by a predetermined amount. In this case, the evaporation of the refrigerant in the outdoor heat exchanger 2 can be suppressed, and the pressure of the discharge gas from the compressor 5 can be further reduced.

今回開示された実施の形態はすべての点で例示であって制限的なものではないと考えられるべきである。本発明の範囲は上記した説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。   The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

この発明の一実施の形態による空気調和機の冷房／暖房サイクルを示す図である。It is a figure which shows the cooling / heating cycle of the air conditioner by one Embodiment of this invention. 図１に示した膨張弁の構成を示す断面図である。It is sectional drawing which shows the structure of the expansion valve shown in FIG. 図１に示した空気調和機の電気回路図である。It is an electric circuit diagram of the air conditioner shown in FIG. 図１〜図３に示した空気調和機の動作を例示するフローチャートである。It is a flowchart which illustrates operation | movement of the air conditioner shown in FIGS.

符号の説明Explanation of symbols

１ 室外ユニット、２ 室外熱交換器、３ 室外送風機、４ 四方弁、５ 圧縮機、６ 膨張弁、７，８ サーミスタ、１０ 室内ユニット、１１ 室内熱交換器、１２ 室内送風機、２０ 弁本体、２１ 弁座、２２ 弁棒、２３ 横銅管、２４ 下銅管、２５ ステッピングモータ、２６ ロータ、２７ ステータ、２８ 電磁コイル、３０ 制御部、３１〜３３ スイッチ、３５ インバータ。   DESCRIPTION OF SYMBOLS 1 Outdoor unit, 2 Outdoor heat exchanger, 3 Outdoor fan, 4 Four way valve, 5 Compressor, 6 Expansion valve, 7, 8 Thermistor, 10 Indoor unit, 11 Indoor heat exchanger, 12 Indoor fan, 20 Valve body, 21 Valve seat, 22 Valve rod, 23 Copper pipe, 24 Lower copper pipe, 25 Stepping motor, 26 Rotor, 27 Stator, 28 Electromagnetic coil, 30 Control unit, 31-33 Switch, 35 Inverter.

Claims (6)

各々が空気と冷媒の熱交換を行なう第１および第２の熱交換器、
それぞれ前記第１および第２の熱交換器に空気を送る第１および第２の送風機、
前記第１の熱交換器で蒸発した冷媒を圧縮して前記第２の熱交換器に与える圧縮機、
前記第２の熱交換器で液化された冷媒を減圧して前記第１の熱交換器に与える膨張弁、
前記膨張弁の入口と出口の圧力差を検出する検出手段、および
前記検出手段によって検出された圧力差が予め定められた値を超えたことに応じて前記圧縮機の駆動周波数を低下させる制御手段を備える、空気調和機。 First and second heat exchangers each for heat exchange between air and refrigerant;
First and second blowers for sending air to the first and second heat exchangers, respectively
A compressor that compresses the refrigerant evaporated in the first heat exchanger and applies the compressed refrigerant to the second heat exchanger;
An expansion valve that depressurizes the refrigerant liquefied in the second heat exchanger and applies the refrigerant to the first heat exchanger;
Detection means for detecting the pressure difference between the inlet and outlet of the expansion valve, and control means for lowering the drive frequency of the compressor in response to the pressure difference detected by the detection means exceeding a predetermined value An air conditioner. 前記検出手段は、前記膨張弁の入口と出口の温度差を検出し、
前記制御手段は、前記検出手段によって検出された温度差が予め定められた温度差を超えた場合に前記膨張弁の入口と出口の圧力差が前記予め定められた値を超えたと判断する、請求項１に記載の空気調和機。 The detecting means detects a temperature difference between an inlet and an outlet of the expansion valve;
The control means determines that the pressure difference between the inlet and outlet of the expansion valve exceeds the predetermined value when the temperature difference detected by the detecting means exceeds a predetermined temperature difference. Item 2. The air conditioner according to Item 1. 前記制御手段は、前記検出手段によって検出された圧力差が前記予め定められた値を超えている場合は、前記圧縮機の駆動周波数を所定時間毎に所定周波数ずつ低下させる、請求項１または請求項２に記載の空気調和機。   The said control means reduces the drive frequency of the said compressor by predetermined frequency every predetermined time, when the pressure difference detected by the said detection means exceeds the said predetermined value. Item 3. An air conditioner according to Item 2. 前記制御手段は、前記検出手段によって検出された圧力差が前記予め定められた値を超えたことに応じて、前記圧縮機の駆動周波数を低下させるとともに、前記第１の送風機の送風能力を低下させる、請求項１から請求項３までのいずれかに記載の空気調和機。   The control means lowers the driving frequency of the compressor and lowers the blowing capacity of the first blower in response to the pressure difference detected by the detection means exceeding the predetermined value. The air conditioner according to any one of claims 1 to 3, wherein: 前記膨張弁は、弁座と、該弁座の中心線に沿って移動可能に設けられた弁棒とを含み、
前記膨張弁の入口は、前記弁棒の長さ方向に設けられ、
前記膨張弁の出口は、前記弁棒の長さ方向と直交する方向に設けられている、請求項１から請求項４までのいずれかに記載の空気調和機。 The expansion valve includes a valve seat and a valve rod provided to be movable along a center line of the valve seat;
The inlet of the expansion valve is provided in the length direction of the valve stem;
The air conditioner according to any one of claims 1 to 4, wherein an outlet of the expansion valve is provided in a direction orthogonal to a length direction of the valve rod. 前記第１の熱交換器は室外に設けられ、前記第２の熱交換器は室内に設けられている、請求項１から請求項５までのいずれかに記載の空気調和機。   The air conditioner according to any one of claims 1 to 5, wherein the first heat exchanger is provided outdoors and the second heat exchanger is provided indoors.
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014159953A (en) * 2014-04-28 2014-09-04 Panasonic Corp Refrigeration cycle device
JP2015180851A (en) * 2015-07-24 2015-10-15 パナソニックＩｐマネジメント株式会社 Refrigeration cycle device
WO2019003306A1 (en) * 2017-06-27 2019-01-03 三菱電機株式会社 Air conditioning device
CN111981627A (en) * 2020-07-17 2020-11-24 珠海格力电器股份有限公司 Liquid flow noise control method and device and air conditioning system
CN114087741A (en) * 2021-11-29 2022-02-25 珠海格力电器股份有限公司 Control method and device of electronic throttling element, storage medium and air conditioner

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6266942B2 (en) * 2013-10-10 2018-01-24 日立ジョンソンコントロールズ空調株式会社 Air conditioner

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06101938A (en) * 1992-08-27 1994-04-12 Hitachi Ltd Expansion valve
JPH06213518A (en) * 1993-01-13 1994-08-02 Hitachi Ltd Heat pump type air conditioner for mixed refrigerant
JPH08152208A (en) * 1994-11-25 1996-06-11 Mitsubishi Electric Corp Refrigerant-circulating system, and refrigerating and air-conditioner apparatus
JPH09243183A (en) * 1996-03-12 1997-09-16 Hitachi Ltd Air conditioner
JP2000346495A (en) * 1999-06-01 2000-12-15 Mitsubishi Electric Corp Throttle device
JP2001280763A (en) * 2000-03-30 2001-10-10 Mitsubishi Electric Corp Refrigerating and air conditioning system
JP2002130770A (en) * 2000-10-30 2002-05-09 Mitsubishi Electric Corp Refrigerating cycle device and its control method
JP2004012127A (en) * 2003-10-02 2004-01-15 Mitsubishi Electric Corp Refrigerator using inflammable refrigerant
JP2004293797A (en) * 2003-02-06 2004-10-21 Saginomiya Seisakusho Inc Throttle valve device and air conditioner
JP2005069644A (en) * 2003-08-27 2005-03-17 Daikin Ind Ltd Multi-stage electric expansion valve and refrigerator

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06101938A (en) * 1992-08-27 1994-04-12 Hitachi Ltd Expansion valve
JPH06213518A (en) * 1993-01-13 1994-08-02 Hitachi Ltd Heat pump type air conditioner for mixed refrigerant
JPH08152208A (en) * 1994-11-25 1996-06-11 Mitsubishi Electric Corp Refrigerant-circulating system, and refrigerating and air-conditioner apparatus
JPH09243183A (en) * 1996-03-12 1997-09-16 Hitachi Ltd Air conditioner
JP2000346495A (en) * 1999-06-01 2000-12-15 Mitsubishi Electric Corp Throttle device
JP2001280763A (en) * 2000-03-30 2001-10-10 Mitsubishi Electric Corp Refrigerating and air conditioning system
JP2002130770A (en) * 2000-10-30 2002-05-09 Mitsubishi Electric Corp Refrigerating cycle device and its control method
JP2004293797A (en) * 2003-02-06 2004-10-21 Saginomiya Seisakusho Inc Throttle valve device and air conditioner
JP2005069644A (en) * 2003-08-27 2005-03-17 Daikin Ind Ltd Multi-stage electric expansion valve and refrigerator
JP2004012127A (en) * 2003-10-02 2004-01-15 Mitsubishi Electric Corp Refrigerator using inflammable refrigerant

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014159953A (en) * 2014-04-28 2014-09-04 Panasonic Corp Refrigeration cycle device
JP2015180851A (en) * 2015-07-24 2015-10-15 パナソニックＩｐマネジメント株式会社 Refrigeration cycle device
WO2019003306A1 (en) * 2017-06-27 2019-01-03 三菱電機株式会社 Air conditioning device
CN111981627A (en) * 2020-07-17 2020-11-24 珠海格力电器股份有限公司 Liquid flow noise control method and device and air conditioning system
CN111981627B (en) * 2020-07-17 2021-07-13 珠海格力电器股份有限公司 Liquid flow noise control method and device and air conditioning system
CN114087741A (en) * 2021-11-29 2022-02-25 珠海格力电器股份有限公司 Control method and device of electronic throttling element, storage medium and air conditioner

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