JP5343618B2

JP5343618B2 - Refrigeration cycle equipment

Info

Publication number: JP5343618B2
Application number: JP2009042324A
Authority: JP
Inventors: ▲祥▼▲隆▼ 久米; 輝彦平; 康伸伊藤
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2009-02-25
Filing date: 2009-02-25
Publication date: 2013-11-13
Anticipated expiration: 2029-02-25
Also published as: JP2010196975A

Abstract

<P>PROBLEM TO BE SOLVED: To suppress generation of noise in stopping an operation of a compressor in a refrigerating cycle apparatus. <P>SOLUTION: This refrigerating cycle apparatus includes the electric compressor 10 for sucking and compressing a refrigerant, a water-refrigerant heat exchanger 11 radiating heat from the high-pressure refrigerant discharged from the compressor 10, an electric expansion valve 12 for decompressing and expanding the refrigerant at a downstream side of the water-refrigerant heat exchanger 11 and capable of adjusting its throttle opening, an evaporator 13 for evaporating the refrigerant decompressed and expanded by the expansion valve 12, an air blowing fan 130 for blowing air to the evaporator 13, and a control means 40 for controlling the rotational frequency of the compressor 10, the operation of the air blowing fan 130, and the expansion valve 12. The control means 40 is constituted to perform a compressor stopping control to gradually lower the rotational frequency of the compressor 10, then gradually increase the throttle opening of the expansion valve 12, and then stop the compressor 10, in stopping the operation of the compressor 10. Further, the operation of the air blowing fan 130 is continued until the predetermined prescribed conditions are established from the start of the compressor stopping control. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、蒸発器に空気を送風する送風機を備える冷凍サイクル装置に関する。 The present invention relates to a refrigeration cycle apparatus including a blower that blows air to an evaporator.

従来、制御装置から指令に基づいて冷凍サイクル装置の圧縮機の作動を停止する場合、圧縮機を直ちに停止すると、冷凍サイクル内の高圧冷媒と低圧冷媒の差圧が大きいために圧縮機等の冷凍サイクル装置の構成部品に作用する負荷が増大する。そして、冷凍サイクル装置の構成部品に作用する負荷増大に伴って、騒音や振動が発生するといった問題があった。 Conventionally, when the operation of the compressor of the refrigeration cycle apparatus is stopped based on a command from the control apparatus, if the compressor is immediately stopped, the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant in the refrigeration cycle is large, so The load acting on the components of the cycle device increases. And there existed a problem that a noise and a vibration generate | occur | produced with the load increase which acts on the component of a refrigerating-cycle apparatus.

この対策として、圧縮機の作動を停止する際には、圧縮機の回転数を徐々に低下させて、冷凍サイクル内の高圧冷媒と低圧冷媒との差圧が充分に小さくなった状態で圧縮機を停止させるものがある（例えば、特許文献１参照）。また、圧縮機の作動を停止する際に、膨張弁の絞り開度を開放側に増大させ、冷凍サイクル内の高圧冷媒と低圧冷媒との差圧が充分に小さくなった状態で圧縮機を停止させるものもある（例えば、特許文献２参照）。 As a countermeasure, when the operation of the compressor is stopped, the compressor speed is gradually decreased so that the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant in the refrigeration cycle is sufficiently small. (For example, refer to Patent Document 1). Also, when stopping the operation of the compressor, increase the throttle opening of the expansion valve to the open side, stop the compressor in a state where the differential pressure between the high-pressure refrigerant and low-pressure refrigerant in the refrigeration cycle has become sufficiently small Some of them (for example, see Patent Document 2).

特開平９−６０９９０号公報Japanese Patent Laid-Open No. 9-60990 特開２００３−２０４７号公報JP 2003-2047 A

ところで、引用文献１に記載のように、圧縮機の作動を停止する際に圧縮機の回転数を徐々に低下させる場合、一般的には、電力消費を抑えるために、圧縮機の作動とは無関係に蒸発器に空気を送風する送風機を停止させている。この場合、送風機が停止しているにもかかわらず圧縮機の作動が継続されるため、蒸発器内に流入した冷媒が蒸発器にて蒸発しないまま圧縮機側に流出してしまう。 By the way, as described in Cited Document 1, when the rotation speed of the compressor is gradually reduced when the operation of the compressor is stopped, in general, in order to reduce power consumption, Irrespectively, the blower that blows air to the evaporator is stopped. In this case, since the operation of the compressor is continued even though the blower is stopped, the refrigerant that has flowed into the evaporator flows out to the compressor side without being evaporated in the evaporator.

また、引用文献２に記載のように、圧縮機の作動を停止する際に、膨張弁の絞り開度を増大させる場合、膨張弁の絞り開度の増大に伴い蒸発器に流入する冷媒流量が増加して、蒸発器に流入した液相冷媒が蒸発しないまま圧縮機側に流出してしまう。 Further, as described in the cited document 2, when the throttle opening of the expansion valve is increased when the operation of the compressor is stopped, the flow rate of the refrigerant flowing into the evaporator with the increase of the throttle opening of the expansion valve is increased. As a result, the liquid refrigerant flowing into the evaporator flows out to the compressor side without evaporating.

このように圧縮機の作動停止に伴い蒸発器の冷媒出口から液相冷媒が流出すると、蒸発器と圧縮機間の冷媒流路を液相冷媒が通過する際の液相冷媒の通過音（液相冷媒通過音）が大きな騒音になるといった問題がある。 As described above, when the liquid-phase refrigerant flows out from the refrigerant outlet of the evaporator due to the stoppage of the operation of the compressor, the passing sound of the liquid-phase refrigerant when the liquid-phase refrigerant passes through the refrigerant flow path between the evaporator and the compressor (liquid (Phase refrigerant passing sound) becomes a loud noise.

本発明は上記点に鑑みて、冷凍サイクル装置において圧縮機の作動を停止する際の騒音の発生を抑制することを目的とする。 In view of the above points, an object of the present invention is to suppress the generation of noise when stopping the operation of a compressor in a refrigeration cycle apparatus.

上記目的を達成するため、請求項１または２に記載の発明では、冷媒を吸入圧縮して吐出する電動圧縮機（１０）と、電動圧縮機（１０）から吐出された高圧冷媒の放熱を行う放熱器（１１）と、放熱器（１１）下流側の冷媒を減圧膨張させるとともに、放熱器（１１）下流側の冷媒通路の通路開度を調整可能な減圧手段（１２）と、減圧手段（１２）で減圧膨張された冷媒を蒸発させる蒸発器（１３）と、蒸発器（１３）に空気を送風する送風機（１３０）と、電動圧縮機（１０）の回転数、送風機（１３０）の作動、および減圧手段（１２）を制御する制御手段（４０）とを備え、制御手段（４０）は、電動圧縮機（１０）の作動を停止させる際に、電動圧縮機（１０）の回転数を徐々に低下させるとともに、減圧手段（１２）にて放熱器（１１）下流側の冷媒通路の通路開度を徐々に増大させてから電動圧縮機（１０）を停止させる圧縮機停止制御を行うように構成され、さらに、圧縮機停止制御が開始されてから予め設定された所定条件が成立するまでの間、送風機（１３０）の作動を継続させることを特徴とする。 In order to achieve the above object, in the first or second aspect of the invention, the electric compressor (10) that sucks and compresses the refrigerant and discharges the high-pressure refrigerant discharged from the electric compressor (10). A radiator (11), a decompression means (12) capable of decompressing and expanding the refrigerant on the downstream side of the radiator (11), and adjusting a passage opening degree of the refrigerant passage on the downstream side of the radiator (11); 12) the evaporator (13) that evaporates the refrigerant expanded under reduced pressure, the blower (130) that blows air to the evaporator (13), the rotational speed of the electric compressor (10), and the operation of the blower (130) And a control means (40) for controlling the decompression means (12), and the control means (40) determines the rotational speed of the electric compressor (10) when stopping the operation of the electric compressor (10). Decrease gradually and release heat with decompression means (12) (11) It is configured to perform compressor stop control for stopping the electric compressor (10) after gradually increasing the passage opening degree of the downstream refrigerant passage, and further, after the compressor stop control is started. The operation of the blower (130) is continued until a predetermined condition set in advance is satisfied.

これによれば、制御手段（４０）にて、圧縮機停止制御が開始されてから所定条件が成立するまでの間、送風機（１３０）の作動を継続させており、その間蒸発器（１３）に流入した冷媒を蒸発させることができるので、蒸発器（１３）と電動圧縮機（１０）の間の冷媒通路に液相冷媒が通過することを抑制することができ、電動圧縮機（１０）の作動を停止する際の騒音の発生を抑制することができる。 According to this, the operation of the blower (130) is continued by the control means (40) from when the compressor stop control is started until the predetermined condition is satisfied, during which the evaporator (13) Since the refrigerant that has flowed in can be evaporated, it is possible to prevent the liquid-phase refrigerant from passing through the refrigerant passage between the evaporator (13) and the electric compressor (10), and the electric compressor (10) Generation of noise when the operation is stopped can be suppressed.

また、請求項３に記載の発明では、冷媒を吸入圧縮して吐出する電動圧縮機（１０）と、電動圧縮機（１０）から吐出された高圧冷媒の放熱を行う放熱器（１１）と、放熱器（１１）下流側の冷媒を減圧膨張させるとともに、放熱器（１１）下流側の冷媒通路の通路開度を調整可能な減圧手段（１２）と、減圧手段（１２）で減圧膨張された冷媒を蒸発させる蒸発器（１３）と、蒸発器（１３）に空気を送風する送風機（１３０）と、電動圧縮機（１０）の回転数、および送風機（１３０）の作動、および減圧手段（１２）を制御する制御手段（４０）とを備え、制御手段（４０）は、電動圧縮機（１０）の作動を停止させる際に、減圧手段（１２）にて放熱器（１１）下流側の冷媒通路の通路開度を徐々に増大させてから電動圧縮機（１０）を停止させる圧縮機停止制御を行うように構成され、さらに、圧縮機停止制御が開始されてから予め設定された所定条件が成立するまでの間、送風機（１３０）の作動を継続させることを特徴とする。 In the invention according to claim 3 , the electric compressor (10) that sucks and compresses and discharges the refrigerant, the radiator (11) that radiates heat of the high-pressure refrigerant discharged from the electric compressor (10), While the refrigerant on the downstream side of the radiator (11) was decompressed and expanded, the decompression means (12) capable of adjusting the passage opening degree of the refrigerant passage on the downstream side of the radiator (11) and the decompression means (12) were decompressed and expanded. The evaporator (13) for evaporating the refrigerant, the blower (130) for blowing air to the evaporator (13), the rotational speed of the electric compressor (10), the operation of the blower (130), and the decompression means (12 Control means (40) for controlling the electric compressor (10), and when the operation of the electric compressor (10) is stopped, the control means (40) is a refrigerant on the downstream side of the radiator (11) by the decompression means (12). After gradually increasing the passage opening of the passage, the electric compressor (10 The compressor is controlled to stop the compressor, and further, the operation of the blower (130) is continued until the predetermined condition is established after the compressor stop control is started. And

このように、減圧手段（１２）にて蒸発器（１１）下流側の冷媒通路の通路開度を徐々に増大させから電動圧縮機（１０）を停止させる圧縮機停止制御を行う場合であっても、圧縮機停止制御が開始されてから所定条件が成立するまでの間、送風機（１３０）の作動を継続させるので、蒸発器（１３）に流入した冷媒を蒸発させることができ、電動圧縮機（１０）の作動を停止する際の騒音の発生を抑制することができる。 As described above, the decompression means (12) performs compressor stop control for stopping the electric compressor (10) after gradually increasing the opening degree of the refrigerant passage on the downstream side of the evaporator (11). Since the operation of the blower (130) is continued until the predetermined condition is satisfied after the compressor stop control is started, the refrigerant flowing into the evaporator (13) can be evaporated, and the electric compressor Generation of noise when the operation of (10) is stopped can be suppressed.

また、請求項４に記載の発明では、冷媒を吸入圧縮して吐出する電動圧縮機（１０）と、電動圧縮機（１０）から吐出された高圧冷媒の放熱を行う放熱器（１１）と、放熱器（１１）下流側の冷媒を減圧膨張させるとともに、放熱器（１１）下流側の冷媒通路の通路開度を調整可能な減圧手段（１２）と、減圧手段（１２）で減圧膨張された冷媒を蒸発させる蒸発器（１３）と、蒸発器（１３）に空気を送風する送風機（１３０）と、電動圧縮機（１０）の回転数、送風機（１３０）の作動、および減圧手段（１２）を制御する制御手段（４０）とを備え、制御手段（４０）は、電動圧縮機（１０）の作動を停止させる際に、電動圧縮機（１０）の回転数を徐々に低下させてから電動圧縮機（１０）を停止させる圧縮機停止制御を行うように構成され、さらに、圧縮機停止制御が開始されてから予め設定された所定条件が成立するまでの間、送風機（１３０）の作動を継続させることを特徴とする。 In the invention according to claim 4 , the electric compressor (10) that sucks and compresses and discharges the refrigerant, the radiator (11) that radiates the high-pressure refrigerant discharged from the electric compressor (10), While the refrigerant on the downstream side of the radiator (11) was decompressed and expanded, the decompression means (12) capable of adjusting the passage opening degree of the refrigerant passage on the downstream side of the radiator (11) and the decompression means (12) were decompressed and expanded. The evaporator (13) for evaporating the refrigerant, the blower (130) for blowing air to the evaporator (13), the rotational speed of the electric compressor (10), the operation of the blower (130), and the decompression means (12) The control means (40) controls the electric compressor (10), and when the operation of the electric compressor (10) is stopped, the control means (40) To perform compressor stop control to stop the compressor (10) Made are further until the compressor stop control has been set in advance since the start predetermined condition is satisfied, characterized in that to continue the operation of the blower (130).

このように、電動圧縮機（１０）の回転数を徐々に低下させてから電動圧縮機（１０）を停止させる圧縮機停止制御を行う場合であっても、圧縮機停止制御が開始されてから所定条件が成立するまでの間、送風機（１３０）の作動を継続させるので、蒸発器（１３）に流入した冷媒を蒸発させることができ、電動圧縮機（１０）の作動を停止する際の騒音の発生を抑制することができる。 As described above, even when the compressor stop control is performed to stop the electric compressor (10) after gradually reducing the rotation speed of the electric compressor (10), the compressor stop control is started. Since the operation of the blower (130) is continued until the predetermined condition is satisfied, the refrigerant flowing into the evaporator (13) can be evaporated, and noise when stopping the operation of the electric compressor (10) Can be suppressed.

ここで、電動圧縮機（１０）の回転数が低くなるとともに、放熱器（１１）下流側の冷媒通路の通路開度が増大すると、冷凍サイクル内の高圧冷媒と低圧冷媒の差圧が小さくなるので、冷凍サイクル内を循環する冷媒流量も低下する。そして、冷凍サイクル内を循環する冷媒流量が低下すると、蒸発器（１３）から流出する液相冷媒の流量も低下することになる。そのため、送風機（１３０）の作動を継続するか否かの所定条件を電動圧縮機（１０）の回転数および放熱器（１１）下流側の冷媒通路の通路開度を基準とすることができる。 Here, when the rotation speed of the electric compressor (10) decreases and the opening degree of the refrigerant passage on the downstream side of the radiator (11) increases, the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant in the refrigeration cycle decreases. Therefore, the flow rate of the refrigerant circulating in the refrigeration cycle is also reduced. And if the flow volume of the refrigerant | coolant which circulates in the refrigerating cycle falls, the flow volume of the liquid phase refrigerant | coolant which flows out from an evaporator (13) will also fall. Therefore, the predetermined condition as to whether or not to continue the operation of the blower (130) can be based on the rotational speed of the electric compressor (10) and the passage opening degree of the refrigerant passage on the downstream side of the radiator (11).

そこで、請求項１に記載の発明では、所定条件は、電動圧縮機（１０）の回転数が、圧縮機停止制御の開始時における回転数よりも低い回転数に設定された基準回転数以下となるとともに、放熱器（１１）下流側の冷媒通路の通路開度が、圧縮機停止制御の開始時における開度よりも大きい開度に設定された基準開度以上となった場合に成立するように設定されていることを特徴とする。 Therefore, in the invention according to claim 1, Jo Tokoro conditions, the rotational speed of the electric compressor (10) is less than the reference rotation speed set to the rotation speed lower than the rotation speed at the start of the compressor stop control And the passage opening degree of the refrigerant passage on the downstream side of the radiator (11) is established when the opening degree is larger than the reference opening degree set larger than the opening degree at the start of the compressor stop control. It is set as follows.

これによれば、送風機（１３０）の作動を継続する所定条件として電動圧縮機（１０）の回転数のみを基準とする場合に比べて、送風機（１３０）の作動の継続時間を長くなる場合があり、より効果的に蒸発器（１３）に流入した冷媒を蒸発させ続けることができる。 According to this, as compared with the case where only the rotation speed of the electric compressor (10) is used as a reference as a predetermined condition for continuing the operation of the blower (130), the duration of the operation of the blower (130) may be longer. Yes, it is possible to continue evaporating the refrigerant that has flowed into the evaporator (13) more effectively.

また、電動圧縮機（１０）の吐出側の高圧冷媒の冷媒圧力および冷媒温度が低下すると、冷凍サイクル内の高圧冷媒と低圧冷媒の差圧が小さくなり、冷凍サイクル内を循環する冷媒流量も低下する。そして、冷凍サイクル内を循環する冷媒流量が低下すると、蒸発器（１３）から流出する液相冷媒の流量も低下することになる。そのため、送風機（１０）の作動を継続するか否かの条件として電動圧縮機（１０）の吐出側の冷媒圧力および冷媒温度を基準とすることができる。 Further, when the refrigerant pressure and the refrigerant temperature of the high-pressure refrigerant on the discharge side of the electric compressor (10) are reduced, the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant in the refrigeration cycle is reduced, and the refrigerant flow rate circulating in the refrigeration cycle is also reduced. To do. And if the flow volume of the refrigerant | coolant which circulates in the refrigerating cycle falls, the flow volume of the liquid phase refrigerant | coolant which flows out from an evaporator (13) will also fall. Therefore, the refrigerant pressure and the refrigerant temperature on the discharge side of the electric compressor (10) can be used as a reference as a condition for continuing the operation of the blower (10).

そこで、請求項２ないし４に記載の発明では、電動圧縮機（１０）の吐出側の高圧冷媒の冷媒圧力若しくは冷媒温度を検出する物理量検出手段（３０）を備え、所定条件は、物理量検出手段（３０）の検出値が、圧縮機停止制御の開始時における高圧冷媒の冷媒圧力若しくは冷媒温度よりも低い冷媒圧力若しくは冷媒温度に設定された基準値以下となった場合に成立するように設定されていることを特徴とする。 Therefore, in the invention according to claims 2 to 4, electrostatic dynamic physical quantity detecting means for detecting the refrigerant pressure or the refrigerant temperature of the high-pressure refrigerant on the discharge side of the compressor (10) comprises a (30), the predetermined condition is physical quantity This is established when the detection value of the detection means (30) is equal to or lower than the reference value set for the refrigerant pressure or refrigerant temperature lower than the refrigerant pressure or refrigerant temperature of the high-pressure refrigerant at the start of compressor stop control. It is characterized by being set.

なお、この欄および特許請求の範囲で記載した各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。 In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

第１実施形態に係るヒートポンプ式給湯機の全体構成図である。1 is an overall configuration diagram of a heat pump hot water heater according to a first embodiment. 第１実施形態に係る圧縮機停止運転を行なう場合の冷凍サイクル装置の各部の作動を示すタイミングチャートである。It is a timing chart which shows the action | operation of each part of the refrigerating-cycle apparatus in the case of performing the compressor stop driving | operation which concerns on 1st Embodiment. 冷凍サイクル装置にて発生する騒音の変化を説明する説明図である。It is explanatory drawing explaining the change of the noise which generate | occur | produces in a refrigeration cycle apparatus. 第１実施形態に係る除霜停止運転を行なう場合の冷凍サイクル装置の各部の作動を示すタイミングチャートである。It is a timing chart which shows the operation | movement of each part of the refrigerating-cycle apparatus in the case of performing the defrost stop driving | operation which concerns on 1st Embodiment. 第２実施形態に係る圧縮機停止運転を行なう場合の冷凍サイクル装置の各部の作動を示すタイミングチャートである。It is a timing chart which shows the action | operation of each part of the refrigerating-cycle apparatus in the case of performing the compressor stop driving | operation which concerns on 2nd Embodiment. 第３実施形態に係る圧縮機停止運転を行なう場合の冷凍サイクル装置の各部の作動を示すタイミングチャートである。It is a timing chart which shows the action | operation of each part of the refrigerating-cycle apparatus in the case of performing the compressor stop driving | operation which concerns on 3rd Embodiment. 第４実施形態に係る圧縮機停止運転を行なう場合の冷凍サイクル装置の各部の作動を示すタイミングチャートである。It is a timing chart which shows operation of each part of a refrigerating cycle device in the case of performing compressor stop operation concerning a 4th embodiment.

（第１実施形態）
以下、本発明の第１実施形態について図１〜図４に基づいて説明する。第１実施形態では、本発明の冷凍サイクル装置をヒートポンプ式給湯機（以下、給湯機と略称する。）に適用した例について説明する。図１は、本実施形態の給湯機の全体構成図である。 (First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1st Embodiment demonstrates the example which applied the refrigerating-cycle apparatus of this invention to the heat pump type hot water heater (henceforth abbreviated as a hot water heater). FIG. 1 is an overall configuration diagram of a water heater according to the present embodiment.

本実施形態の給湯機は、冷媒を循環させる冷凍サイクル装置と後述する貯湯タンク２０内の給湯水を循環させる給湯回路とに大別される。 The water heater of this embodiment is roughly classified into a refrigeration cycle apparatus that circulates refrigerant and a hot water supply circuit that circulates hot water in a hot water storage tank 20 described later.

図１に示すように、冷凍サイクル装置は、圧縮機１０、水冷媒熱交換器１１、電気式膨張弁１２、蒸発器１３を主な構成要素として備え、これら冷凍サイクル装置の機能部品１０〜１３は、冷媒配管１４にて順次接続されている。この冷凍サイクル装置では、冷媒として二酸化炭素を採用しており、圧縮機１０から吐出された高圧冷媒の圧力が冷媒の臨界圧力以上となる超臨界蒸気圧縮式冷凍サイクルを構成している。 As shown in FIG. 1, the refrigeration cycle apparatus includes a compressor 10, a water refrigerant heat exchanger 11, an electric expansion valve 12, and an evaporator 13 as main components, and functional components 10 to 13 of these refrigeration cycle apparatuses. Are sequentially connected by a refrigerant pipe 14. This refrigeration cycle apparatus employs carbon dioxide as a refrigerant, and constitutes a supercritical vapor compression refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 10 is equal to or higher than the critical pressure of the refrigerant.

圧縮機１０は、冷凍サイクル装置において冷媒を吸入し、臨界圧力以上となるまで圧縮して吐出するもので、吐出容量が固定された固定容量型圧縮機１０ａを電動モータ１０ｂにて駆動する電動圧縮機である。固定容量型圧縮機１０ａとしては、例えば、スクロール型圧縮機構やベーン型圧縮機構などの各種圧縮機構を採用することができる。 The compressor 10 sucks the refrigerant in the refrigeration cycle apparatus, compresses and discharges the refrigerant until the pressure becomes equal to or higher than the critical pressure, and electrically compresses the fixed capacity compressor 10a having a fixed discharge capacity by the electric motor 10b. Machine. As the fixed capacity type compressor 10a, for example, various compression mechanisms such as a scroll type compression mechanism and a vane type compression mechanism can be adopted.

電動モータ１０ｂは、後述する制御装置４０から出力される制御信号によって、その作動（回転数）が制御されるもので、交流モータ、直流モータのいずれの形式を採用してもよい。そして回転数制御によって圧縮機１０の冷媒吐出能力が変更される。 The operation (rotation speed) of the electric motor 10b is controlled by a control signal output from the control device 40 to be described later, and either an AC motor or a DC motor may be adopted. And the refrigerant | coolant discharge capability of the compressor 10 is changed by rotation speed control.

圧縮機１０の冷媒吐出口には、水冷媒熱交換器１１の冷媒通路１１ａ入口側が接続されている。水冷媒熱交換器１１は、圧縮機１０から吐出された高温高圧冷媒が通過する冷媒通路１１ａと給湯水が通過する給湯水通路１１ｂとを有し、圧縮機１０吐出冷媒の熱と給湯水とを熱交換させることで給湯水の温度を昇温させる熱交換器である。従って、水冷媒熱交換器１１は、圧縮機１０吐出冷媒の熱を放熱する放熱器として機能する。 The refrigerant discharge port of the compressor 10 is connected to the refrigerant passage 11 a inlet side of the water refrigerant heat exchanger 11. The water-refrigerant heat exchanger 11 includes a refrigerant passage 11a through which high-temperature and high-pressure refrigerant discharged from the compressor 10 passes, and a hot-water supply passage 11b through which hot-water supply passes. It is a heat exchanger which raises the temperature of hot water by exchanging heat. Therefore, the water refrigerant heat exchanger 11 functions as a radiator that radiates the heat of the refrigerant discharged from the compressor 10.

なお、本実施形態の水冷媒熱交換器１１の冷媒通路１１ａにおける冷媒の流れ方向と給湯水通路１１ｂにおける給湯水の流れ方向は、互いに対向する方向となるようになっている。このように、水冷媒熱交換器１１における冷媒の流れ方向と給湯水の流れ方向を互いに対向する方向とすれば、冷媒通路１１ａを流通する冷媒と給湯水通路１１ｂを流通する給湯水との温度差を確保して熱交換効率を向上させることができる。 In addition, the flow direction of the refrigerant in the refrigerant passage 11a of the water-refrigerant heat exchanger 11 of the present embodiment and the flow direction of the hot water in the hot water supply passage 11b are opposite to each other. Thus, if the flow direction of the refrigerant and the flow direction of the hot water in the water-refrigerant heat exchanger 11 are opposite to each other, the temperature of the refrigerant flowing through the refrigerant passage 11a and the hot water flowing through the hot water supply passage 11b The difference can be secured to improve the heat exchange efficiency.

また、本実施形態の冷凍サイクル装置では、圧縮機１０吐出冷媒の圧力が臨界圧力以上となる超臨界冷凍サイクルを構成しているので、水冷媒熱交換器１１の冷媒通路１１ａを通過する冷媒は、凝縮することなく超臨界状態のまま放熱する。 In the refrigeration cycle apparatus of the present embodiment, a supercritical refrigeration cycle in which the pressure of the refrigerant discharged from the compressor 10 is equal to or higher than the critical pressure constitutes the refrigerant passing through the refrigerant passage 11a of the water refrigerant heat exchanger 11. The heat is dissipated in a supercritical state without condensing.

水冷媒熱交換器１１の冷媒通路１１ａ出口側には、電気式膨張弁１２の入口側が接続されている。電気式膨張弁１２は冷媒通路１１ａから流出した高圧冷媒を減圧膨張させる減圧手段を構成するとともに、水冷媒熱交換器１１下流側の冷媒通路の通路開度を調整する調整手段でもある。 The inlet side of the electric expansion valve 12 is connected to the outlet side of the refrigerant passage 11 a of the water refrigerant heat exchanger 11. The electric expansion valve 12 constitutes a decompression means for decompressing and expanding the high-pressure refrigerant flowing out from the refrigerant passage 11a, and is also an adjusting means for adjusting the passage opening degree of the refrigerant passage on the downstream side of the water refrigerant heat exchanger 11.

より具体的には、この電気式膨張弁１２は、絞り開度を調整可能な弁体部１２ａと、この弁体部１２ａの絞り開度を可変制御するサーボモータからなる電動アクチュエータ１２ｂとを有して構成される。ここで、電動アクチュエータ１２ｂは、絞り開度を全閉（絞り開度≒０％）、中間開度（０％＜絞り開度＜１００％）、全開（絞り開度≒１００％）に調整可能に構成されている。なお、電動アクチュエータ１２ｂは、後述する制御装置４０から出力される制御信号によって、その作動が制御される。 More specifically, the electric expansion valve 12 has a valve body 12a that can adjust the throttle opening, and an electric actuator 12b that includes a servo motor that variably controls the throttle opening of the valve body 12a. Configured. Here, the electric actuator 12b can adjust the throttle opening to be fully closed (throttle opening≈0%), intermediate opening (0% <throttle opening <100%), fully open (throttle opening≈100%). It is configured. The operation of the electric actuator 12b is controlled by a control signal output from the control device 40 described later.

電気式膨張弁１２の出口側には、蒸発器１３が接続されている。蒸発器１３は、電気式膨張弁１２にて減圧された低圧冷媒と外気（室外空気）とを熱交換させることで、低圧冷媒を蒸発させて吸熱作用を発揮させる吸熱用熱交換器として機能する。そして、蒸発器１３の冷媒出口側には、圧縮機１０の冷媒吸入口が接続されている。 An evaporator 13 is connected to the outlet side of the electric expansion valve 12. The evaporator 13 functions as an endothermic heat exchanger that evaporates the low-pressure refrigerant and exerts an endothermic effect by exchanging heat between the low-pressure refrigerant decompressed by the electric expansion valve 12 and the outside air (outdoor air). . A refrigerant inlet of the compressor 10 is connected to the refrigerant outlet side of the evaporator 13.

ここで、蒸発器１３は、電動モータ１３０ａにて駆動される送風ファン１３０を備えており、この送風ファン１３０により蒸発器１３に向かって外気が送風される。なお、送風ファン１３０の電動モータ１３０ａは、後述する冷凍サイクル用制御装置４１から出力される制御信号によって、その作動が制御される。 Here, the evaporator 13 includes a blower fan 130 driven by an electric motor 130 a, and outside air is blown toward the evaporator 13 by the blower fan 130. The operation of the electric motor 130a of the blower fan 130 is controlled by a control signal output from the refrigeration cycle control device 41 described later.

また、本実施形態の冷凍サイクル装置は、圧縮機１０の出口側と蒸発器１３の入口側とを接続するバイパス回路１５、およびバイパス回路１５を開閉する電磁式の除霜用開閉弁１６を備えている。この除霜用開閉弁１６は、後述する制御装置４０から出力される制御信号によって、その作動が制御される。 The refrigeration cycle apparatus of the present embodiment also includes a bypass circuit 15 that connects the outlet side of the compressor 10 and the inlet side of the evaporator 13, and an electromagnetic defrosting on-off valve 16 that opens and closes the bypass circuit 15. ing. The operation of the defrosting on-off valve 16 is controlled by a control signal output from the control device 40 described later.

次に、給湯回路について説明すると、給湯回路は、水冷媒熱交換器１１にて加熱された高温の温水を蓄える貯湯タンク２０、水冷媒熱交換器１１と貯湯タンク２０とを接続する水配管２１、および水配管２１の途中に設置されて水冷媒熱交換器１１と貯湯タンク２０との間で水を循環させる循環ポンプ２２等から構成されている。 Next, the hot water supply circuit will be described. The hot water supply circuit includes a hot water storage tank 20 that stores high-temperature hot water heated by the water refrigerant heat exchanger 11, and a water pipe 21 that connects the water refrigerant heat exchanger 11 and the hot water storage tank 20. And a circulation pump 22 that is installed in the middle of the water pipe 21 and circulates water between the water refrigerant heat exchanger 11 and the hot water storage tank 20.

また、貯湯タンク２０には、水道水等を給水するための給水配管（図示せず）が接続され、さらに台所、洗面所、風呂等の給湯対象機器に給湯するための給湯配管（図示せず）が接続されている。ここで、循環ポンプ２２は、後述する制御装置４０から出力される制御信号によって、その作動が制御される電動式のポンプである。 The hot water storage tank 20 is connected to a water supply pipe (not shown) for supplying tap water or the like, and further a hot water supply pipe (not shown) for supplying hot water to a hot water supply target device such as a kitchen, a washroom, or a bath. ) Is connected. Here, the circulation pump 22 is an electric pump whose operation is controlled by a control signal output from a control device 40 described later.

次に、本実施形態の電気制御部の概要について説明する。本実施形態の電気制御部は、制御装置４０として、冷凍サイクル用制御装置（冷凍サイクル用ＥＣＵ）４１および給湯用制御装置（給湯用ＥＣＵ）４２を備えている。冷凍サイクル用制御装置４１および給湯用制御装置４２は、それぞれ、ＣＰＵ、ＲＯＭ、ＲＡＭ等を含む周知のマイクロコンピュータおよびその周辺回路等により構成されている。 Next, an outline of the electric control unit of the present embodiment will be described. The electric control unit of the present embodiment includes a refrigeration cycle control device (refrigeration cycle ECU) 41 and a hot water supply control device (hot water supply ECU) 42 as the control device 40. The refrigeration cycle control device 41 and the hot water supply control device 42 are each configured by a known microcomputer including a CPU, a ROM, a RAM, and the like, and peripheral circuits thereof.

冷凍サイクル用制御装置４１の出力側には、圧縮機１０の電動モータ１０ｂ、電気式膨張弁１２の電動アクチュエータ１２ｂ、送風ファン１３０の電動モータ１３０ａ、除霜用開閉弁１６等が接続され、これらの機器の作動を制御する。 Connected to the output side of the refrigeration cycle control device 41 are the electric motor 10b of the compressor 10, the electric actuator 12b of the electric expansion valve 12, the electric motor 130a of the blower fan 130, the defrosting on-off valve 16, and the like. Control the operation of the equipment.

また、冷凍サイクル用制御装置４１の入力側には、圧縮機１０吐出側の冷媒圧力を検出する高圧側圧力センサ３０、蒸発器１３の入口側の冷媒温度を検出する蒸発器温度センサ３１等が接続され、これらセンサの検出信号が入力される。なお、高圧側圧力センサ３０が本発明の物理量検出手段に相当し、蒸発器温度センサ３１が本発明の蒸発器温度検出手段に相当する。 Further, on the input side of the control device 41 for the refrigeration cycle, there are a high pressure side pressure sensor 30 for detecting the refrigerant pressure on the discharge side of the compressor 10, an evaporator temperature sensor 31 for detecting the refrigerant temperature on the inlet side of the evaporator 13 , and the like. Connected and detection signals of these sensors are input. The high pressure side pressure sensor 30 corresponds to the physical quantity detection means of the present invention, and the evaporator temperature sensor 31 corresponds to the evaporator temperature detection means of the present invention.

一方、給湯用制御装置４２の出力側には、給湯回路の循環ポンプ２２等が接続され、循環ポンプ２２等の作動を制御する。また、給湯用制御装置４２の入力側には、水冷媒熱交換器１１の給湯水通路１１ｂ出口側の給湯水温度を検出する沸き上げ温度センサ３２、貯湯タンク２０と循環ポンプ２２間の給湯水温度を検出する給湯水温度センサ３３等が接続され、これらセンサの検出信号が入力される。 On the other hand, the circulation pump 22 of the hot water supply circuit is connected to the output side of the hot water supply control device 42 to control the operation of the circulation pump 22 and the like. Further, on the input side of the hot water supply control device 42, a boiling temperature sensor 32 for detecting the hot water temperature at the outlet side of the hot water passage 11 b of the water refrigerant heat exchanger 11, and hot water between the hot water storage tank 20 and the circulation pump 22 are provided. A hot water temperature sensor 33 for detecting temperature is connected, and detection signals from these sensors are input.

さらに、冷凍サイクル用制御装置４１の入力側には、操作パネル３４が接続され、冷凍サイクル装置を含む給湯機の作動・停止の操作信号、給湯水の目標給湯温度設定信号等が入力される。 Further, an operation panel 34 is connected to the input side of the control device 41 for the refrigeration cycle, and an operation signal for operating / stopping the hot water heater including the refrigeration cycle device, a target hot water supply temperature setting signal, and the like are input.

ここで、冷凍サイクル用制御装置４１および給湯用制御装置４２は、互いに電気的に接続されており、通信可能に構成されている。これにより、一方の制御装置に入力された検出信号および操作信号に基づいて、他方の制御装置が上述の各種アクチュエータ等の作動を制御することもできる。従って、冷凍サイクル用制御装置４１および給湯用制御装置４２を１つの制御装置として一体的に構成してもよい。 Here, the control device 41 for refrigeration cycle and the control device 42 for hot water supply are electrically connected to each other and configured to be able to communicate with each other. Thereby, based on the detection signal and operation signal which were input into one control apparatus, the other control apparatus can also control operation | movement of the above-mentioned various actuators. Therefore, the refrigeration cycle control device 41 and the hot water supply control device 42 may be integrally configured as one control device.

次に、上記の構成における本実施形態の給湯機の作動を説明する。制御装置４０は、電力会社の安価な深夜電力料金が適用される時刻になったり、操作パネル３４から作動信号が入力されたりすると、給湯機を作動させて、貯湯タンク２０内の水を沸き上げる沸き上げ運転を開始させる。 Next, the operation of the water heater of the present embodiment having the above configuration will be described. The control device 40 activates the water heater to boil the water in the hot water storage tank 20 when it is time to apply an inexpensive late-night electricity charge of an electric power company or when an operation signal is input from the operation panel 34. Start boiling operation.

具体的には、循環ポンプ２２を作動させて水冷媒熱交換器１１と貯湯タンク２０との間で水を循環させる。同時に、圧縮機１０を作動させて冷凍サイクル内で冷媒を循環させる。これにより、水冷媒熱交換器１１にて冷媒と水の熱交換が行われ、換言すると、外気から吸熱した熱及び圧縮機１０の圧縮仕事量に相当する熱量が給湯水に与えられ、給湯水が加熱される。なお、沸き上げ運転時には、バイパス回路１５に設けられた除霜用開閉弁１６が閉鎖されており、圧縮機１０から吐出された冷媒は、水冷媒熱交換器１１の冷媒通路１１ａに流れる。 Specifically, the circulation pump 22 is operated to circulate water between the water / refrigerant heat exchanger 11 and the hot water storage tank 20. At the same time, the compressor 10 is operated to circulate the refrigerant in the refrigeration cycle. Thus, heat exchange between the refrigerant and water is performed in the water / refrigerant heat exchanger 11, in other words, heat absorbed from the outside air and heat corresponding to the compression work of the compressor 10 are given to the hot water. Is heated. During the heating operation, the defrosting on-off valve 16 provided in the bypass circuit 15 is closed, and the refrigerant discharged from the compressor 10 flows into the refrigerant passage 11 a of the water refrigerant heat exchanger 11.

そして、制御装置４０は、沸き上げ温度センサ３２等の信号に基づいて、給湯水が所定の温度まで沸き上げられたと判断されると、沸き上げ運転を終了させる。制御装置４０では、沸き上げ運転を終了させる際、すなわち圧縮機１０等の給湯機の各構成部品の作動を停止する際の騒音、振動等の発生を抑制するために圧縮機停止制御を実行する。 When it is determined that the hot water has been heated up to a predetermined temperature based on the signal from the boiling temperature sensor 32 or the like, the control device 40 ends the boiling operation. The control device 40 executes compressor stop control in order to suppress generation of noise, vibration, etc. when the boiling operation is finished, that is, when the operation of each component of the water heater such as the compressor 10 is stopped. .

以下、制御装置４０にて実行する圧縮機停止制御について図２、図３に基づいて説明する。図２は、本実施形態に係る圧縮機停止制御を行う際の冷凍サイクル装置の各部の作動を示すタイミングチャートであり、図３は圧縮機停止制御時の騒音レベルの変化を説明する説明図である。 Hereinafter, the compressor stop control executed by the control device 40 will be described with reference to FIGS. FIG. 2 is a timing chart showing the operation of each part of the refrigeration cycle apparatus when the compressor stop control according to this embodiment is performed, and FIG. 3 is an explanatory diagram for explaining the change in the noise level during the compressor stop control. is there.

先ず、時刻ｔ０では、冷凍サイクル装置等にて沸き上げ運転の作動を継続している（給湯機運転ＯＮ）。具体的には、制御装置４０によって、圧縮機１０の回転数が目標回転数に制御され、電気式膨張弁１２の絞り開度が中間開度に制御され、送風ファン１３０の作動が運転状態（ＯＮ）に制御されている。 First, at time t0, the boiling operation is continued in the refrigeration cycle apparatus or the like (hot water supply operation ON). Specifically, the control device 40 controls the rotational speed of the compressor 10 to the target rotational speed, the throttle opening degree of the electric expansion valve 12 is controlled to an intermediate opening degree, and the operation of the blower fan 130 is in an operating state ( ON).

次に、時刻ｔ１にて、沸き上げ温度センサ３２等の信号に基づいて給湯水が所定の温度まで沸き上げられると、制御装置４０にて、沸き上げ運転を終了させるために圧縮機停止制御を開始する（給湯機運転ＯＦＦ）。 Next, when hot water is boiled up to a predetermined temperature based on a signal from the boiling temperature sensor 32 or the like at time t1, the controller 40 performs compressor stop control in order to end the boiling operation. Start (water heater operation OFF).

本実施形態の圧縮機停止制御では、圧縮機１０が回転停止（回転数≒０）するまで回転数を徐々に低下させるとともに、電気式膨張弁１２の絞り開度が１００％（全開）となるまで絞り開度を徐々に増大させる。具体的に制御装置４０は、単位時間あたりの圧縮機１０の回転数の低下割合が一定となるように電動モータ１０ｂを制御するとともに、単位時間あたりの電気式膨張弁１２の絞り開度の増加割合が一定となるように電動アクチュエータ１２ｂを制御する。本実施形態では、圧縮機１０が回転停止（回転数≒０）する時刻ｔ２となると、圧縮機停止制御を終了する。 In the compressor stop control of the present embodiment, the rotational speed is gradually reduced until the compressor 10 stops rotating (rotational speed≈0), and the throttle opening of the electric expansion valve 12 becomes 100% (fully open). The throttle opening is gradually increased until Specifically, the control device 40 controls the electric motor 10b so that the rate of decrease in the rotation speed of the compressor 10 per unit time is constant, and increases the throttle opening of the electric expansion valve 12 per unit time. The electric actuator 12b is controlled so that the ratio is constant. In the present embodiment, the compressor stop control is terminated at time t2 when the compressor 10 stops rotating (rotation speed≈0).

ここで、制御装置４０では、圧縮機停止制御を開始してから所定の停止条件が成立するまでの間、送風ファン１３０の作動が継続するように制御している。 Here, the control device 40 performs control so that the operation of the blower fan 130 continues from when the compressor stop control is started until a predetermined stop condition is satisfied.

具体的には、本実施形態の送風ファン１３０の停止条件は、圧縮機１０が回転停止となった否かを条件とし、圧縮機１０が回転停止（回転数≒０）となった場合に条件が成立するようになっている。 Specifically, the stop condition of the blower fan 130 of the present embodiment is based on whether or not the compressor 10 has stopped rotating, and is a condition when the compressor 10 stops rotating (rotation number≈0). Is supposed to hold.

換言すると、本実施形態の送風ファン１３０は、圧縮機停止制御の開始時刻ｔ１から圧縮機１０が回転停止する時刻ｔ２までの間、その作動を継続するように制御されている。なお、圧縮機１０の回転停止（回転数）は、例えば、制御装置４０からの出力信号に基づいて検出したり、圧縮機１０の回転数を検出する回転数検出センサを配置してセンサの出力に基づいて検出したりすることができる。 In other words, the blower fan 130 of the present embodiment is controlled so as to continue its operation from the start time t1 of the compressor stop control to the time t2 when the compressor 10 stops rotating. The rotation stop (rotation speed) of the compressor 10 is detected based on, for example, an output signal from the control device 40, or a rotation speed detection sensor for detecting the rotation speed of the compressor 10 is arranged to output the sensor. Or can be detected based on.

ところで、従来までの給湯機の冷凍サイクル装置では、制御装置４０にて沸き上げ運転を終了させる際、すなわち時刻ｔ１となると、圧縮機１０の作動とは無関係に送風ファン１３０の作動を運転停止（ＯＦＦ）するように制御されていた。 By the way, in the conventional refrigeration cycle apparatus for a water heater, when the boiling operation is terminated by the control device 40, that is, at time t1, the operation of the blower fan 130 is stopped regardless of the operation of the compressor 10 ( OFF).

そして、図３に示すように、従来の給湯機の冷凍サイクル装置では、圧縮機停止制御の開始時刻ｔ１となると圧縮機１０の回転数の低下に伴い一旦騒音レベルが低下し始める。しかし、蒸発器１３の送風ファン１３０が停止しており、蒸発器１３内の液冷媒が蒸発器１３の出口側から流出し、蒸発器１３と圧縮機１０の間の冷媒通路に液相冷媒が流れる。これにより、蒸発器１３と圧縮機１０の間の冷媒通路にて液相冷媒の通過音が生じるので、一旦低下した騒音レベルが増大してしまう問題が発生する。 As shown in FIG. 3, in the conventional refrigeration cycle apparatus for a hot water heater, the noise level once begins to decrease with a decrease in the rotational speed of the compressor 10 at the start time t1 of the compressor stop control. However, the blower fan 130 of the evaporator 13 is stopped, the liquid refrigerant in the evaporator 13 flows out from the outlet side of the evaporator 13, and the liquid phase refrigerant flows into the refrigerant passage between the evaporator 13 and the compressor 10. Flowing. Thereby, since the passage sound of the liquid phase refrigerant is generated in the refrigerant passage between the evaporator 13 and the compressor 10, there arises a problem that the noise level once lowered increases.

これに対して、本実施形態の給湯機の冷凍サイクル装置では、圧縮機停止制御の開始時刻ｔ１から圧縮機１０が回転停止する時刻ｔ２となるまで、送風ファン１３０の作動を継続している。そのため、圧縮機停止制御を開始後においても、蒸発器１３に流入した冷媒を蒸発させることができるので、蒸発器１３と圧縮機１０の間の冷媒通路に液相冷媒が通過してしまうことを抑制することができる。従って、従来よりも圧縮機１０の作動を停止する際の騒音の発生を抑制することができる。 On the other hand, in the refrigeration cycle apparatus for a hot water supply apparatus of the present embodiment, the operation of the blower fan 130 is continued from the start time t1 of the compressor stop control until the time t2 at which the compressor 10 stops rotating. Therefore, even after the compressor stop control is started, the refrigerant flowing into the evaporator 13 can be evaporated, so that the liquid-phase refrigerant passes through the refrigerant passage between the evaporator 13 and the compressor 10. Can be suppressed. Therefore, it is possible to suppress the generation of noise when the operation of the compressor 10 is stopped as compared with the conventional case.

また、本実施形態では、圧縮機停止制御を行う際に、送風ファン１３０の作動を継続して蒸発器１３内の冷媒を蒸発させているので、低圧側の冷媒圧力を上昇させることができるので、冷凍サイクル内の高圧冷媒と低圧冷媒の差圧をより早く均圧化させることができる。そのため、圧縮機１０の停止までの時間の短縮を図ることができ、圧縮機停止制御に必要とされる時間を短縮することができ、圧縮機停止制御に伴う電力消費を低減することができる。 Further, in the present embodiment, when the compressor stop control is performed, the refrigerant in the evaporator 13 is evaporated by continuing the operation of the blower fan 130, so the refrigerant pressure on the low pressure side can be increased. The pressure difference between the high-pressure refrigerant and the low-pressure refrigerant in the refrigeration cycle can be equalized more quickly. Therefore, the time until the compressor 10 is stopped can be shortened, the time required for the compressor stop control can be shortened, and the power consumption accompanying the compressor stop control can be reduced.

さらに、本実施形態では、圧縮機停止制御を行っている際にも、蒸発器１３にて液相冷媒を蒸発させることができるので、次回、圧縮機１０を起動する際において圧縮機１０で液相冷媒を圧縮してしまうことを抑制することができる。これにより、圧縮機１０起動時の負荷を低減することも可能となる。 Further, in the present embodiment, since the liquid-phase refrigerant can be evaporated by the evaporator 13 even when the compressor stop control is being performed, the compressor 10 is operated by the compressor 10 when the compressor 10 is started next time. Compressing the phase refrigerant can be suppressed. Thereby, it becomes possible to reduce the load at the time of starting the compressor 10.

ところで、上述の冷凍サイクル装置では、低外気温時等に蒸発器１３に霜が付着することから、所定条件が成立すると制御装置４０にて除霜運転を実行するように各部の作動が制御される。なお、除霜運転を開始するための所定条件は、外気温、蒸発器１３内の冷媒温度等が所定温度まで低下することで条件が成立するようになっている。 By the way, in the above-described refrigeration cycle apparatus, since frost adheres to the evaporator 13 at a low outside air temperature or the like, the operation of each part is controlled so that the defrosting operation is executed by the control device 40 when a predetermined condition is satisfied. The The predetermined conditions for starting the defrosting operation are established when the outside air temperature, the refrigerant temperature in the evaporator 13 and the like are lowered to a predetermined temperature.

この除霜運転では、所定条件が成立して運転を開始すると、圧縮機１０の運転を開始するとともに、圧縮機１０の回転数を目標回転数に制御し、電気式膨張弁１２の絞り開度を全閉（絞り開度≒０％）する。また、除霜用開閉弁１６を開弁させてバイパス回路１５を全開し、圧縮機１０から吐出される高温高圧冷媒が蒸発器１３に流れるようにする。このように圧縮機１０から吐出される高温高圧冷媒が蒸発器１３に流れるようにすることで、蒸発器１３に付着した霜を溶かしている。そして、蒸発器１３に付着した霜が溶けると除霜運転を終了させる。 In this defrosting operation, when the predetermined condition is established and the operation is started, the operation of the compressor 10 is started, the rotation speed of the compressor 10 is controlled to the target rotation speed, and the throttle opening degree of the electric expansion valve 12 is controlled. Is fully closed (throttle opening ≈ 0%). Further, the defrosting on-off valve 16 is opened to fully open the bypass circuit 15 so that the high-temperature and high-pressure refrigerant discharged from the compressor 10 flows to the evaporator 13. Thus, the frost adhering to the evaporator 13 is melted by allowing the high-temperature and high-pressure refrigerant discharged from the compressor 10 to flow into the evaporator 13. And if the frost adhering to the evaporator 13 melt | dissolves, a defrost operation will be complete | finished.

ここで、除霜運転を終了させる際に、圧縮機１０の運転を直ちに停止すると沸き上げ運転時のように騒音、振動が発生してしまう。そのため、図４に示すように、沸き上げ運転の圧縮機停止制御と同様に、除霜運転を終了する際にも、圧縮機１０が回転停止（回転数≒０）するまで回転数を徐々に低下させるとともに、電気式膨張弁１２の絞り開度が１００％（全開）となるまで絞り開度を徐々に増大させる。さらに、圧縮機１０の回転停止するまで送風ファン１３０の作動を継続する。これにより、除霜運転を終了させる際の騒音の発生を抑制することができる。 Here, when the defrosting operation is terminated, if the operation of the compressor 10 is immediately stopped, noise and vibration are generated as in the boiling operation. Therefore, as shown in FIG. 4, as with the compressor stop control in the boiling operation, when the defrosting operation is terminated, the rotational speed is gradually increased until the compressor 10 stops rotating (the rotational speed ≈ 0). While decreasing, the throttle opening is gradually increased until the throttle opening of the electric expansion valve 12 reaches 100% (fully open). Further, the operation of the blower fan 130 is continued until the rotation of the compressor 10 is stopped. Thereby, generation | occurrence | production of the noise at the time of complete | finishing a defrost operation can be suppressed.

しかし、除霜運転を終了する際に冷凍サイクル内の電気式膨張弁１２の絞り開度が充分に開いていない状態で除霜用開閉弁１６を直ちに閉弁するように制御すると、冷凍サイクル内の高圧冷媒の圧力が急上昇してしまうため、冷凍サイクル装置の負荷が増大する。 However, when the defrosting on / off valve 16 is controlled to be immediately closed when the throttle opening of the electric expansion valve 12 in the refrigeration cycle is not sufficiently opened when the defrosting operation is finished, Since the pressure of the high-pressure refrigerant suddenly rises, the load on the refrigeration cycle apparatus increases.

そのため、本実施形態では、電気式膨張弁１２の絞り開度が充分に開弁された後（本実施形態では、全開となった後）に、除霜用開閉弁１６を閉弁するように制御している。より詳しくは、図４に示すように、圧縮機１０を回転停止するタイミングで除霜用開閉弁１６を閉弁するように制御している。これにより、除霜運転を終了する際の冷凍サイクル装置の負荷増大を抑制することができる。 Therefore, in the present embodiment, the defrosting on-off valve 16 is closed after the throttle opening degree of the electric expansion valve 12 is sufficiently opened (in the present embodiment, after being fully opened). I have control. More specifically, as shown in FIG. 4, the defrosting on-off valve 16 is controlled to close at the timing when the compressor 10 stops rotating. Thereby, the load increase of the refrigerating-cycle apparatus at the time of complete | finishing a defrost operation can be suppressed.

（第２実施形態）
次に、本発明の第２実施形態について図５に基づいて説明する。図５は第２実施形態に係る圧縮機停止制御を行う際の冷凍サイクル装置の各部の作動を示すタイミングチャートを示している。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. FIG. 5 is a timing chart showing the operation of each part of the refrigeration cycle apparatus when performing compressor stop control according to the second embodiment.

第１実施形態と比較して、第２実施形態は、主に圧縮機停止制御における送風ファン１３０の停止条件が異なっている。そのため、上記第１実施形態と同様または均等な部分について同一の符号を付し、その説明を省略する。 Compared with the first embodiment, the second embodiment differs mainly in the stop condition of the blower fan 130 in the compressor stop control. Therefore, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof is omitted.

図５に示すように、第２実施形態の圧縮機停止制御では、圧縮機１０の回転数が予め設定された基準回転数となるまで回転数を徐々に低下させ、圧縮機１０の回転数が基準回転数以下となると電動モータ１０ｂをオフして圧縮機１０を回転停止させるようにしている。 As shown in FIG. 5, in the compressor stop control of the second embodiment, the rotational speed is gradually decreased until the rotational speed of the compressor 10 reaches a preset reference rotational speed, and the rotational speed of the compressor 10 is reduced. When the rotation speed is equal to or lower than the reference rotation speed, the electric motor 10b is turned off to stop the rotation of the compressor 10.

つまり、圧縮機停止制御を行う際の送風ファン１３０の停止条件が、圧縮機１０の回転数が予め設定された基準回転数以下となった場合に条件が成立するようになっている。ここで、基準回転数は、圧縮機停止制御の開始時の回転数よりも低い回転数に設定されている。より詳しくは、圧縮機１０を直ちに停止したとしても圧縮機に作用する負荷が低負荷となる程度の回転数に設定されており、例えば、圧縮機１０の最大回転数の１０％以内の回転数に設定することができる。 That is, the condition is established when the stop condition of the blower fan 130 when the compressor stop control is performed is equal to or lower than the reference rotation speed set in advance. Here, the reference rotation speed is set to a rotation speed lower than the rotation speed at the start of the compressor stop control. More specifically, even if the compressor 10 is immediately stopped, the rotation speed is set so that the load acting on the compressor becomes a low load. For example, the rotation speed is within 10% of the maximum rotation speed of the compressor 10. Can be set to

これによれば、送風ファン１３０は、制御装置４０によって圧縮機停止制御の開始時刻ｔ１から圧縮機１０が基準回転数以下となる時刻ｔ３までの間、その作動を継続するように制御されている。従って、圧縮機停止制御の開始時刻ｔ１から圧縮機１０が基準回転数以下となる時刻ｔ３までの間、蒸発器１３に流入した冷媒を蒸発させることができるので、圧縮機１０の作動を停止する際の騒音の発生を抑制することができる。 According to this, the blower fan 130 is controlled by the control device 40 so as to continue its operation from the start time t1 of the compressor stop control to the time t3 when the compressor 10 becomes equal to or lower than the reference rotation speed. . Accordingly, since the refrigerant flowing into the evaporator 13 can be evaporated from the start time t1 of the compressor stop control to the time t3 when the compressor 10 becomes equal to or lower than the reference rotation speed, the operation of the compressor 10 is stopped. The generation of noise at the time can be suppressed.

（第３実施形態）
次に、第３実施形態について図６に基づいて説明する。図６は第３実施形態に係る圧縮機停止制御を行う際の冷凍サイクル装置の各部の作動を示すタイミングチャートを示している。なお、第２実施形態と同様に、第３実施形態についても上記第１実施形態と同様または均等な部分について同一の符号を付し、その説明を省略する。 (Third embodiment)
Next, a third embodiment will be described with reference to FIG. FIG. 6 is a timing chart showing the operation of each part of the refrigeration cycle apparatus when performing compressor stop control according to the third embodiment. As in the second embodiment, the same reference numerals are given to the same or equivalent parts in the third embodiment as in the first embodiment, and the description thereof is omitted.

第３実施形態の圧縮機停止制御では、圧縮機１０の回転数が回転停止となるまで回転数を徐々に低下させて圧縮機１０を回転停止させるようにしている。 In the compressor stop control according to the third embodiment, the rotation speed of the compressor 10 is gradually decreased until the rotation speed of the compressor 10 is stopped.

ここで、図６に示すように、圧縮機停止制御の開始時において圧縮機１０の回転数が最大回転数よりも低い回転数となっている場合には、圧縮機１０の回転停止までの時刻ｔ２となるまでに電気式膨張弁１２の絞り開度が全開しない状況が想定される。 Here, as shown in FIG. 6, when the rotation speed of the compressor 10 is lower than the maximum rotation speed at the start of the compressor stop control, the time until the rotation of the compressor 10 is stopped. It is assumed that the throttle opening degree of the electric expansion valve 12 is not fully opened until t2.

そこで、第３実施形態では、圧縮機停止制御を行う際の送風ファン１３０の停止条件を、圧縮機１０の回転数に加えて、電気式膨張弁１２の絞り開度が全開となった否かを条件としている。つまり、圧縮機１０の回転数が回転停止となり、電気式膨張弁１２の絞り開度が全開となった場合に送風ファン１３０の停止条件が成立するようにしている。なお、基準回転数は第２実施形態で説明した内容と同様に設定されている。 Therefore, in the third embodiment, whether or not the throttle opening degree of the electric expansion valve 12 is fully opened is added to the stop condition of the blower fan 130 when the compressor stop control is performed in addition to the rotation speed of the compressor 10. Is a condition. That is, the stop condition of the blower fan 130 is established when the rotation speed of the compressor 10 is stopped and the throttle opening of the electric expansion valve 12 is fully opened. The reference rotational speed is set in the same manner as described in the second embodiment.

これによれば、圧縮機停止制御の開始時刻ｔ１から圧縮機１０が回転停止となる時刻ｔ２までの期間が短い場合であっても、電気式膨張弁１２の絞り開度が全開となるまでの時刻ｔ４となるまでの間、送風ファン１３０の作動を継続させることができる。 According to this, even when the period from the start time t1 of the compressor stop control to the time t2 at which the compressor 10 stops rotating is short, the throttle opening of the electric expansion valve 12 is fully opened. The operation of the blower fan 130 can be continued until time t4.

従って、圧縮機停止制御の開始時において圧縮機１０の回転数が低い回転数であったとしても、長い期間、蒸発器１３に流入した冷媒を蒸発させることができるので、圧縮機１０の作動を停止する際の騒音の発生をより効果的に抑制することができる。 Therefore, even if the rotation speed of the compressor 10 is low at the start of the compressor stop control, the refrigerant flowing into the evaporator 13 can be evaporated for a long period of time. Generation of noise when stopping can be more effectively suppressed.

ここで、第３実施形態における送風ファン１３０の停止条件のうち圧縮機１０の回転数に関しては、第２実施形態と同様に基準回転数以下となった場合に、条件が成立するようにしてもよい。 Here, regarding the rotation speed of the compressor 10 among the stop conditions of the blower fan 130 in the third embodiment, the condition may be satisfied when the rotation speed is equal to or lower than the reference rotation speed as in the second embodiment. Good.

また、電気式膨張弁１２の絞り開度に関しては、全開となった場合に限らず、予め設定した基準開度にまで増大した場合に条件が成立するようにしてもよい。なお、基準開度は、圧縮機停止制御の開始時の開度よりも大きい開度に設定されている。 Further, the throttle opening of the electric expansion valve 12 is not limited to being fully opened, but may be satisfied when the throttle opening is increased to a preset reference opening. The reference opening is set to an opening larger than the opening at the start of compressor stop control.

より詳しくは、電気式膨張弁１２を直ちに全開したとしても蒸発器１３に流入する冷媒の流量が実質的に変化しない程度の開度に設定され、例えば、９０％以上の開度に設定することができる。なお、電気式膨張弁１２の絞り開度は、例えば、制御装置４０からの出力信号に基づいて検出したり、電気式膨張弁１２の絞り開度を検出するセンサの出力に基づいて検出したりすることができる。 More specifically, even if the electric expansion valve 12 is immediately fully opened, the opening degree is set such that the flow rate of the refrigerant flowing into the evaporator 13 does not substantially change, for example, the opening degree is set to 90% or more. Can do. The throttle opening of the electric expansion valve 12 is detected based on, for example, an output signal from the control device 40, or detected based on the output of a sensor that detects the throttle opening of the electric expansion valve 12. can do.

（第４実施形態）
次に、第４実施形態について図７に基づいて説明する。図７は第４実施形態に係る圧縮機停止制御を行う際の冷凍サイクル装置の各部の作動を示すタイミングチャートを示している。なお、第２実施形態と同様に、第４実施形態についても上記第１実施形態と同様または均等な部分について同一の符号を付し、その説明を省略する。 (Fourth embodiment)
Next, a fourth embodiment will be described with reference to FIG. FIG. 7 is a timing chart showing the operation of each part of the refrigeration cycle apparatus when performing compressor stop control according to the fourth embodiment. As in the second embodiment, the same reference numerals are given to the same or equivalent parts in the fourth embodiment as in the first embodiment, and the description thereof is omitted.

第４実施形態では、圧縮機停止制御を行う際の送風ファン１３０の停止条件を、圧縮機停止制御を開始してから予め設定した基準時間を経過した場合に条件が成立するようにしている。 In the fourth embodiment, the condition for stopping the blower fan 130 when the compressor stop control is performed is such that the condition is established when a preset reference time has elapsed since the compressor stop control was started.

ここで、基準時間は、圧縮機停止制御時における圧縮機１０が回転停止するまでの経過時間、電気式膨張弁１２の絞り開度が全開となるまでの経過時間等を予め実験的に計測しておき、これらの経過時間のうち最も長い経過時間以上の時間を設定することができる。 Here, the reference time is experimentally measured in advance such as the elapsed time until the compressor 10 stops rotating during the compressor stop control, the elapsed time until the throttle opening of the electric expansion valve 12 is fully opened, and the like. In addition, a time longer than the longest elapsed time among these elapsed times can be set.

これによれば、圧縮機停止制御の開始時刻ｔ１から圧縮機１０が回転停止となる時刻ｔ２までの期間、および電気式膨張弁１２の絞り開度が全開となるまでの時刻ｔ４となるまでの期間が短い場合であっても、予め設定された基準時間ｔ５となるまでの間、送風ファン１３０の作動を継続させることができる。 According to this, the period from the start time t1 of the compressor stop control to the time t2 when the compressor 10 stops rotating, and the time t4 until the throttle opening of the electric expansion valve 12 is fully opened. Even if the period is short, the operation of the blower fan 130 can be continued until the preset reference time t5 is reached.

従って、圧縮機停止制御の開始時において圧縮機１０の回転数が低い回転数、および電気式膨張弁１２の絞り開度が全開に近い状態であったとしても、長い期間、蒸発器１３に流入した冷媒を蒸発させることができるので、圧縮機１０の作動を停止する際の騒音の発生をより効果的に抑制することができる。 Therefore, even when the rotation speed of the compressor 10 is low and the throttle opening degree of the electric expansion valve 12 is almost fully opened at the start of the compressor stop control, it flows into the evaporator 13 for a long period. Therefore, the generation of noise when the operation of the compressor 10 is stopped can be more effectively suppressed.

（第５実施形態）
次に、第５実施形態について説明する。なお、第２実施形態と同様に、第５実施形態についても上記第１実施形態と同様または均等な部分について同一の符号を付し、その説明を省略する。 (Fifth embodiment)
Next, a fifth embodiment will be described. As in the second embodiment, the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals in the fifth embodiment, and the description thereof is omitted.

第５実施形態では、蒸発器１３内の冷媒が気液２相状態から気相状態へと推移すると、急激に冷媒温度が上昇する傾向に着目して圧縮機停止制御を行う際の送風ファン１３０の停止条件を設定している。 In the fifth embodiment, when the refrigerant in the evaporator 13 transitions from the gas-liquid two-phase state to the gas phase state, the blower fan 130 when performing the compressor stop control paying attention to the tendency of the refrigerant temperature to rise suddenly. The stop condition is set.

具体的には、圧縮機停止制御を行う際の送風ファン１３０の停止条件を、蒸発器温度センサ３１で検出した蒸発器１３の冷媒温度が基準温度以上となった場合に条件が成立するようにしている。なお、基準温度は、蒸発器１３内に液相冷媒が存在する場合の冷媒温度よりも高い温度に設定されている。 Specifically, the stop condition of the blower fan 130 when performing the compressor stop control is such that the condition is established when the refrigerant temperature of the evaporator 13 detected by the evaporator temperature sensor 31 is equal to or higher than the reference temperature. ing. The reference temperature is set to a temperature higher than the refrigerant temperature when the liquid phase refrigerant is present in the evaporator 13.

本実施形態では、蒸発器１３の冷媒温度を基準として、圧縮機停止制御を行う際の送風ファン１３０の停止条件を設定することで、蒸発器１３内の液相冷媒が蒸発した後に、送風ファン１３０の作動を停止させることができる。 In the present embodiment, by setting the stop condition of the blower fan 130 when the compressor stop control is performed based on the refrigerant temperature of the evaporator 13, the blower fan after the liquid-phase refrigerant in the evaporator 13 evaporates. The operation of 130 can be stopped.

ここで、蒸発器温度センサ３１は、蒸発器１３の入口側の冷媒温度を検出するように蒸発器１３の入口側に配置されており（図１参照）、蒸発器１３に流入した冷媒が気相状態となった後に、送風ファン１３０の作動を停止することになる。 Here, the evaporator temperature sensor 31 is arranged on the inlet side of the evaporator 13 so as to detect the refrigerant temperature on the inlet side of the evaporator 13 (see FIG. 1), and the refrigerant flowing into the evaporator 13 is gas. After the phase state is reached, the operation of the blower fan 130 is stopped.

つまり、圧縮機停止制御を開始してから蒸発器１３の入口側の冷媒が気相状態となるまで送風ファン１３０の作動を継続させるため、蒸発器１３内の冷媒が蒸発器１３と圧縮機１０との間の冷媒通路を液冷媒が通過することをより効果的に抑制することができる。 That is, since the operation of the blower fan 130 is continued after the compressor stop control is started until the refrigerant on the inlet side of the evaporator 13 is in a gas phase state, the refrigerant in the evaporator 13 is changed between the evaporator 13 and the compressor 10. It is possible to more effectively suppress the liquid refrigerant from passing through the refrigerant passage therebetween.

なお、蒸発器温度センサ３１を蒸発器１３の出口側の冷媒温度を検出するように蒸発器１３の出口側に配置された構成としてもよい。この場合、圧縮機停止制御を開始してから蒸発器１３の出口側の冷媒が気相状態となるまで送風ファン１３０の作動を継続させるため、蒸発器１３の入口側の冷媒温度を基準にする場合に比べて、送風ファン１３０の作動時間を短縮することができるため消費電力の増加抑制することができる。 The evaporator temperature sensor 31 may be arranged on the outlet side of the evaporator 13 so as to detect the refrigerant temperature on the outlet side of the evaporator 13. In this case, since the operation of the blower fan 130 is continued after the compressor stop control is started until the refrigerant on the outlet side of the evaporator 13 is in a gas phase state, the refrigerant temperature on the inlet side of the evaporator 13 is used as a reference. Compared to the case, since the operation time of the blower fan 130 can be shortened, an increase in power consumption can be suppressed.

（第６実施形態）
次に、第６実施形態について説明する。なお、第２実施形態と同様に、第６実施形態についても上記第１実施形態と同様または均等な部分について同一の符号を付し、その説明を省略する。 (Sixth embodiment)
Next, a sixth embodiment will be described. As in the second embodiment, the sixth embodiment is also denoted by the same reference numerals for the same or equivalent parts as in the first embodiment, and the description thereof is omitted.

第６実施形態では、圧縮機１０の吐出側の高圧冷媒の冷媒圧力が低下すると、冷凍サイクル内の高圧冷媒と低圧冷媒との差圧が小さくなり、循環する冷媒流量も低下するといった傾向に着目して圧縮機停止制御を行う際の送風ファン１３０の停止条件を設定している。 In the sixth embodiment, attention is paid to the tendency that when the refrigerant pressure of the high-pressure refrigerant on the discharge side of the compressor 10 decreases, the differential pressure between the high-pressure refrigerant and the low-pressure refrigerant in the refrigeration cycle decreases, and the circulating refrigerant flow rate also decreases. Thus, the stop condition of the blower fan 130 when the compressor stop control is performed is set.

具体的には、圧縮機停止制御を行う際の送風ファン１３０の停止条件を、高圧側圧力センサ３０で検出した圧縮機１０吐出側の高圧冷媒の圧力が基準圧力以下となった場合に条件が成立するようにしている。なお、基準圧力は、圧縮機停止制御の開始時の高圧冷媒の圧力よりも低い圧力に設定されており、例えば、予め実験等によって圧縮機１０吐出側の高圧冷媒の圧力と低圧冷媒の圧力との差圧が充分に小さくなった状態の冷媒圧力を設定することができる。 Specifically, the stop condition of the blower fan 130 when the compressor stop control is performed is determined when the pressure of the high-pressure refrigerant on the discharge side of the compressor 10 detected by the high-pressure side pressure sensor 30 is equal to or lower than the reference pressure. It is going to be established. The reference pressure is set to a pressure lower than the pressure of the high-pressure refrigerant at the start of compressor stop control. For example, the pressure of the high-pressure refrigerant on the discharge side of the compressor 10 and the pressure of the low-pressure refrigerant are determined in advance through experiments or the like. It is possible to set the refrigerant pressure in a state where the differential pressure is sufficiently small.

本実施形態では、圧縮機１０の吐出側の高圧冷媒の冷媒圧力を基準として、圧縮機停止制御を行う際の送風ファン１３０の停止条件を設定しているので、冷凍サイクル内を循環する冷媒流量が充分に低下した状態で、送風ファン１３０の作動を停止させることになる。 In the present embodiment, since the stop condition of the blower fan 130 when performing the compressor stop control is set based on the refrigerant pressure of the high-pressure refrigerant on the discharge side of the compressor 10, the refrigerant flow rate circulating in the refrigeration cycle The operation of the blower fan 130 is stopped in a state where the airflow is sufficiently lowered.

つまり、圧縮機停止制御を開始してから圧縮機１０吐出側の高圧冷媒の圧力と低圧冷媒の圧力との差圧が充分に小さくなるまで送風ファン１３０の作動を継続させるため、蒸発器１３内の冷媒が蒸発器１３と圧縮機１０との間の冷媒通路を液冷媒が通過することをより効果的に抑制することができる。 That is, since the operation of the blower fan 130 is continued until the differential pressure between the pressure of the high-pressure refrigerant on the discharge side of the compressor 10 and the pressure of the low-pressure refrigerant becomes sufficiently small after the compressor stop control is started, It is possible to more effectively suppress the liquid refrigerant from passing through the refrigerant passage between the evaporator 13 and the compressor 10.

なお、圧縮機１０吐出側の高圧冷媒の圧力は、冷媒温度と相関関係があるので、例えば、高圧側圧力センサ３０に替えて圧縮機１０吐出側の高圧冷媒の冷媒温度を検出する高圧側温度センサ（図示せず）を配置する構成としてもよい。この場合、圧縮機停止制御を行う際の送風ファン１３０の停止条件を、高圧側温度センサで検出した圧縮機１０吐出側の高圧冷媒の温度が基準温度以下となった場合に条件が成立するようにすればよい。なお、基準温度は、圧縮機停止制御の開始時の高圧冷媒の冷媒温度よりも低い温度に設定されており、例えば、予め実験等によって圧縮機１０吐出側の高圧冷媒の圧力と低圧冷媒の圧力との差圧が充分に小さくなった状態の冷媒温度を設定することができる。 Since the pressure of the high-pressure refrigerant on the discharge side of the compressor 10 has a correlation with the refrigerant temperature, for example, the high-pressure side temperature for detecting the refrigerant temperature of the high-pressure refrigerant on the discharge side of the compressor 10 instead of the high-pressure side pressure sensor 30. It is good also as a structure which arrange | positions a sensor (not shown). In this case, the stop condition of the blower fan 130 when the compressor stop control is performed is such that the condition is established when the temperature of the high-pressure refrigerant on the discharge side of the compressor 10 detected by the high-pressure side temperature sensor is equal to or lower than the reference temperature. You can do it. The reference temperature is set to a temperature lower than the refrigerant temperature of the high-pressure refrigerant at the start of the compressor stop control. For example, the pressure of the high-pressure refrigerant on the discharge side of the compressor 10 and the pressure of the low-pressure refrigerant are experimentally determined in advance. It is possible to set the refrigerant temperature in a state in which the differential pressure between the two is sufficiently small.

（他の実施形態）
以上、本発明の実施例について説明したが、本発明はこれに限定されるものではなく、各請求項に記載した範囲を逸脱しない限り、各請求項の記載文言に限定されず、当業者がそれらから容易に置き換えられる範囲にも及び、かつ、当業者が通常有する知識に基づく改良を適宜付加することができる。例えば、以下のように種々変形可能である。 (Other embodiments)
As mentioned above, although the Example of this invention was described, this invention is not limited to this, Unless it deviates from the range described in each claim, it is not limited to the description word of each claim, and those skilled in the art Improvements based on the knowledge that a person skilled in the art normally has can be added as appropriate to the extent that they can be easily replaced. For example, various modifications are possible as follows.

（１）上述の各実施形態では、水冷媒熱交換器１１下流側の冷媒通路の通路開度を電気式膨張弁１２にて調整する構成としているが、これに限定されない。例えば、水冷媒熱交換器１１と蒸発器１３との間に電気式膨張弁１２を迂回するバイパス回路を設け、このバイパス回路に開閉弁を配置する。そして、圧縮機停止制御時において、バイパス回路に配置した開閉弁の開度を徐々に増大させることで、放熱器下流側の冷媒通路の通路開度を調整する構成としてもよい。この場合、電気式膨張弁１２、バイパス回路、および開閉弁にて減圧手段が構成される。
(1) In each above-mentioned embodiment, although it is set as the structure which adjusts the passage opening degree of the refrigerant path of the water refrigerant heat exchanger 11 downstream by the electric expansion valve 12, it is not limited to this. For example, a bypass circuit that bypasses the electric expansion valve 12 is provided between the water-refrigerant heat exchanger 11 and the evaporator 13, and an open / close valve is disposed in the bypass circuit. And at the time of compressor stop control, it is good also as a structure which adjusts the opening degree of the refrigerant | coolant passage downstream of a radiator by gradually increasing the opening degree of the on-off valve arrange | positioned in the bypass circuit. In this case, the electric expansion valve 12, the bypass circuit, and the on-off valve constitute pressure reducing means.

（２）上述の各実施形態の制御装置４０は、圧縮機停止制御を実行する際に、単位時間あたりの圧縮機１０の回転数の低下割合が一定となるように電動モータ１０ｂを制御しているが、単位時間あたり圧縮機１０の回転数の低下割合を変化させてもよい。また、圧縮機停止制御を実行する際に、単位時間あたりの電気式膨張弁１２の絞り開度の増加割合が一定となるように電動アクチュエータ１２ｂを制御しているが、単位時間あたりの電気式膨張弁１２の絞り開度の増加割合を変化させてもよい。 (2) When executing the compressor stop control, the control device 40 of each of the above embodiments controls the electric motor 10b so that the rate of decrease in the rotation speed of the compressor 10 per unit time is constant. However, the rate of decrease in the rotational speed of the compressor 10 per unit time may be changed. Further, when the compressor stop control is executed, the electric actuator 12b is controlled so that the increase rate of the throttle opening degree of the electric expansion valve 12 per unit time is constant. The increasing rate of the throttle opening degree of the expansion valve 12 may be changed.

（３）上述の各実施形態では、圧縮機停止制御にて、圧縮機１０の回転数を徐々に低下させるとともに、膨張弁１２の絞り開度を徐々に増大させてから圧縮機１０を停止する制御を行っているが、これに限定されるものではない。 (3) In each of the embodiments described above, the compressor 10 is stopped after gradually decreasing the rotation speed of the compressor 10 and gradually increasing the throttle opening of the expansion valve 12 in the compressor stop control. Although control is performed, the present invention is not limited to this.

例えば、圧縮機停止制御にて膨張弁１２の絞り開度を徐々に増大させずに圧縮機１０の回転数を徐々に低下させてから圧縮機１０を停止する制御を行ってもよい。また、圧縮機停止制御にて圧縮機１０の回転数を徐々に低下させずに膨張弁１２の絞り開度を徐々に増大させてから圧縮機１０を停止する制御を行ってもよい。 For example, the compressor stop control may be performed so that the compressor 10 is stopped after the rotational speed of the compressor 10 is gradually decreased without gradually increasing the throttle opening of the expansion valve 12. Further, the compressor stop control may be performed so that the compressor 10 is stopped after the throttle opening of the expansion valve 12 is gradually increased without gradually decreasing the rotation speed of the compressor 10.

いずれの場合であっても、圧縮機停止制御が開始されてから所定条件が成立するまでの間、送風ファン１３０の作動を継続させることで、蒸発器１３に流入した冷媒を蒸発させることができ、圧縮機１０の作動を停止する際の騒音の発生を抑制することができる。 In any case, the refrigerant flowing into the evaporator 13 can be evaporated by continuing the operation of the blower fan 130 until the predetermined condition is satisfied after the compressor stop control is started. The generation of noise when the operation of the compressor 10 is stopped can be suppressed.

（４）上述の実施形態の冷凍サイクル装置に、蒸発器１３から流出した冷媒の気液を分離して、余剰冷媒を蓄える気液分離手段としてのアキュムレータを設けてもよい。なお、アキュムレータを設ける場合、蒸発器１３とアキュムレータ間を液相冷媒が通過する際の冷媒通過音が騒音になる。 (4) The refrigeration cycle apparatus of the above-described embodiment may be provided with an accumulator as a gas-liquid separation unit that separates the gas-liquid refrigerant flowing out of the evaporator 13 and stores excess refrigerant. In addition, when providing an accumulator, the refrigerant | coolant passage sound at the time of a liquid phase refrigerant | coolant passing between the evaporator 13 and an accumulator becomes noise.

（５）上述の各実施形態の冷凍サイクル装置では、冷媒として二酸化炭素を用いて超臨界冷凍サイクルを構成しているが、これに限らず、フロン系、ＨＣ系等の冷媒のように高圧圧力が臨界圧力を超えない冷媒を用いて亜臨界冷凍サイクルを構成してもよい。 (5) In the refrigeration cycle apparatus of each of the above-described embodiments, the supercritical refrigeration cycle is configured using carbon dioxide as a refrigerant. The subcritical refrigeration cycle may be configured using a refrigerant that does not exceed the critical pressure.

（６）上述の各実施形態では、本発明の冷凍サイクル装置をヒートポンプ式給湯機に採用した例について説明したが、これに限定されず、車両用空調装置等に適用してもよい。 (6) In each of the above-described embodiments, the example in which the refrigeration cycle apparatus of the present invention is adopted in a heat pump type hot water heater has been described. However, the present invention is not limited to this and may be applied to a vehicle air conditioner or the like.

１０圧縮機（電動圧縮機）
１１水冷媒熱交換器（放熱器）
１２減圧手段（電気式膨張弁）
１３蒸発器
１３０送風ファン（送風機）
３０高圧側圧力センサ（物理量検出手段）
３１蒸発器温度センサ（蒸発器温度検出手段） 10 Compressor (electric compressor)
11 Water refrigerant heat exchanger (heat radiator)
12 Pressure reducing means (electric expansion valve)
13 Evaporator 130 Blower Fan (Blower)
30 High pressure sensor (physical quantity detection means)
31 Evaporator temperature sensor (Evaporator temperature detection means)

Claims

An electric compressor (10) for sucking and compressing and discharging refrigerant;
A radiator (11) for radiating heat of the high-pressure refrigerant discharged from the electric compressor (10);
A pressure reducing means (12) capable of decompressing and expanding the refrigerant on the downstream side of the radiator (11) and adjusting a passage opening degree of the refrigerant passage on the downstream side of the radiator (11);
An evaporator (13) for evaporating the refrigerant decompressed and expanded by the decompression means (12);
A blower (130) for blowing air to the evaporator (13);
A control means (40) for controlling the number of rotations of the electric compressor (10), the operation of the blower (130), and the pressure reducing means (12),
When the operation of the electric compressor (10) is stopped, the control means (40) gradually decreases the rotational speed of the electric compressor (10), and the heat release by the pressure reducing means (12). The compressor (11) is configured to perform compressor stop control for stopping the electric compressor (10) after gradually increasing the passage opening of the refrigerant passage on the downstream side, and further, the compressor stop control is started. The operation of the blower (130) is continued until a predetermined condition established in advance is established ,
The predetermined condition is that the rotational speed of the electric compressor (10) is equal to or lower than a reference rotational speed set to a rotational speed lower than the rotational speed at the start of the compressor stop control, and the radiator (11 ) It is set so as to be established when the passage opening of the downstream refrigerant passage is equal to or larger than a reference opening set to an opening larger than the opening at the start of the compressor stop control. A refrigeration cycle apparatus according to claim.

An electric compressor (10) for sucking and compressing and discharging refrigerant;
A radiator (11) for radiating heat of the high-pressure refrigerant discharged from the electric compressor (10);
A pressure reducing means (12) capable of decompressing and expanding the refrigerant on the downstream side of the radiator (11) and adjusting a passage opening degree of the refrigerant passage on the downstream side of the radiator (11);
An evaporator (13) for evaporating the refrigerant decompressed and expanded by the decompression means (12);
A blower (130) for blowing air to the evaporator (13);
Control means (40) for controlling the rotational speed of the electric compressor (10), the operation of the blower (130), and the pressure reducing means (12) ;
Physical quantity detection means (30) for detecting the refrigerant pressure or refrigerant temperature of the high-pressure refrigerant on the discharge side of the electric compressor (10) ,
When the operation of the electric compressor (10) is stopped, the control means (40) gradually decreases the rotational speed of the electric compressor (10), and the heat release by the pressure reducing means (12). The compressor (11) is configured to perform compressor stop control for stopping the electric compressor (10) after gradually increasing the passage opening of the refrigerant passage on the downstream side, and further, the compressor stop control is started. The operation of the blower (130) is continued until a predetermined condition established in advance is established ,
The predetermined condition is that a detection value of the physical quantity detection means (30) is equal to or lower than a reference value set to a refrigerant pressure or a refrigerant temperature lower than a refrigerant pressure or a refrigerant temperature of a high-pressure refrigerant at the start of the compressor stop control. The refrigeration cycle apparatus is set so as to be established when it becomes .

An electric compressor (10) for sucking and compressing and discharging refrigerant;
A radiator (11) for radiating heat of the high-pressure refrigerant discharged from the electric compressor (10);
A pressure reducing means (12) capable of decompressing and expanding the refrigerant on the downstream side of the radiator (11) and adjusting a passage opening degree of the refrigerant passage on the downstream side of the radiator (11);
An evaporator (13) for evaporating the refrigerant decompressed and expanded by the decompression means (12);
A blower (130) for blowing air to the evaporator (13);
Control means (40) for controlling the rotational speed of the electric compressor (10), the operation of the blower (130), and the pressure-reducing means (12) ;
Physical quantity detection means (30) for detecting the refrigerant pressure or refrigerant temperature of the high-pressure refrigerant on the discharge side of the electric compressor (10) ,
When the operation of the electric compressor (10) is stopped, the control means (40) gradually increases the opening of the refrigerant passage of the radiator (11) by the pressure reducing means (12). Is configured to perform compressor stop control for stopping the electric compressor (10), and further from the start of the compressor stop control until a predetermined condition is established, the blower ( to continue the operation of the 130),
The predetermined condition is that a detection value of the physical quantity detection means (30) is equal to or lower than a reference value set to a refrigerant pressure or a refrigerant temperature lower than a refrigerant pressure or a refrigerant temperature of a high-pressure refrigerant at the start of the compressor stop control. The refrigeration cycle apparatus is set so as to be established when it becomes .

An electric compressor (10) for sucking and compressing and discharging refrigerant;
A radiator (11) for radiating heat of the high-pressure refrigerant discharged from the electric compressor (10);
A pressure reducing means (12) capable of decompressing and expanding the refrigerant on the downstream side of the radiator (11) and adjusting a passage opening degree of the refrigerant passage on the downstream side of the radiator (11);
An evaporator (13) for evaporating the refrigerant decompressed and expanded by the decompression means (12);
A blower (130) for blowing air to the evaporator (13);
Control means (40) for controlling the number of revolutions of the electric compressor (10), the operation of the blower (130), and the opening degree of the refrigerant passage on the downstream side of the radiator (11) ;
Physical quantity detection means (30) for detecting the refrigerant pressure or refrigerant temperature of the high-pressure refrigerant on the discharge side of the electric compressor (10) ,
When the operation of the electric compressor (10) is stopped, the control means (40) gradually decreases the rotational speed of the electric compressor (10) and then stops the electric compressor (10). The compressor is configured to perform stop control, and further, the operation of the blower (130) is continued from when the compressor stop control is started until a predetermined condition is established ,
The predetermined condition is that a detection value of the physical quantity detection means (30) is equal to or lower than a reference value set to a refrigerant pressure or a refrigerant temperature lower than a refrigerant pressure or a refrigerant temperature of a high-pressure refrigerant at the start of the compressor stop control. The refrigeration cycle apparatus is set so as to be established when it becomes .