JP2015075268A - 冷凍サイクル装置 - Google Patents
冷凍サイクル装置 Download PDFInfo
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- JP2015075268A JP2015075268A JP2013211076A JP2013211076A JP2015075268A JP 2015075268 A JP2015075268 A JP 2015075268A JP 2013211076 A JP2013211076 A JP 2013211076A JP 2013211076 A JP2013211076 A JP 2013211076A JP 2015075268 A JP2015075268 A JP 2015075268A
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- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00642—Control systems or circuits; Control members or indication devices for heating, cooling or ventilating devices
- B60H1/00814—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation
- B60H1/00878—Control systems or circuits characterised by their output, for controlling particular components of the heating, cooling or ventilating installation the components being temperature regulating devices
- B60H1/00899—Controlling the flow of liquid in a heat pump system
- B60H1/00921—Controlling the flow of liquid in a heat pump system where the flow direction of the refrigerant does not change and there is an extra subcondenser, e.g. in an air duct
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- B—PERFORMING OPERATIONS; TRANSPORTING
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- 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
Description
さらに、圧縮機(11)から吐出された高圧冷媒を減圧させるノズル部(21a)から噴射される高速度の噴射冷媒の吸引作用によって、冷媒吸引口(21d)から蒸発器(15)下流側冷媒を吸引し、噴射冷媒と冷媒吸引口(21d)から吸引された吸引冷媒との混合冷媒を昇圧させて、圧縮機(11)の吸入口側へ流出させる昇圧部(21f)を有するエジェクタ(21)を備える冷凍サイクル装置を特徴とする。
以下、図1〜図4を用いて、本発明の第1実施形態について説明する。本実施形態では、本発明に係る蒸気圧縮式の冷凍サイクル装置10を、走行用電動モータから車両走行用の駆動力を得る電気自動車の車両用空調装置1に適用している。冷凍サイクル装置10は、車両用空調装置1において、空調対象空間である車室内へ送風される送風空気を冷却あるいは加熱する機能を果たす。従って、本実施形態の加熱対象流体は送風空気である。
0.3≦Gn/Gr≦0.5…(F1)
なお、吐出冷媒流量Gr、エジェクタ側冷媒流量Gnおよび放熱器側冷媒流量Gcは、いずれも質量流量であり、吐出冷媒流量Grは、エジェクタ側冷媒流量Gnと放熱器側冷媒流量Gcとの合算値となる。
TAO=Kset×Tset−Kr×Tr−Kam×Tam−Ks×As+C…(F2)
なお、Tsetは温度設定スイッチによって設定された車室内設定温度、Trは内気センサによって検出された車室内温度(内気温)、Tamは外気センサによって検出された外気温、Asは日射センサによって検出された日射量である。Kset、Kr、Kam、Ksは制御ゲインであり、Cは補正用の定数である。
冷房運転モードでは、空調制御装置40が、暖房用膨張弁14を全開とし、冷房用膨張弁16を減圧作用を発揮する絞り状態とし、暖房用開閉弁18を閉じ、ノズル部用開閉弁22を閉じる。従って、冷房運転モード時に構成されるサイクル構成は、特許請求の範囲に記載された非昇圧用冷媒回路に含まれる。
除湿暖房運転モードでは、空調制御装置40が、暖房用膨張弁14および冷房用膨張弁16を全開状態あるいは絞り状態とし、暖房用開閉弁18を閉じ、ノズル部用開閉弁22を閉じる。従って、除湿暖房運転モード時に構成されるサイクル構成は、特許請求の範囲に記載された非昇圧用冷媒回路に含まれる。
第1モードは、除湿暖房運転モード時に、目標吹出温度TAOが冷房基準温度α以上、かつ、予め定めた第1基準温度以下となっている場合に実行される。
第2モードは、除湿暖房運転モード時に、目標吹出温度TAOが第1基準温度より高く、かつ、予め定めた第2基準温度以下となった場合に実行される。第2モードでは、空調制御装置40が、暖房用膨張弁14を絞り状態とし、冷房用膨張弁16の絞り開度を第1モード時よりも増加させる。
第3モードは、除湿暖房運転モード時に、目標吹出温度TAOが第2基準温度より高く、かつ、予め定めた第3基準温度以下となった場合に実行される。第3モードでは、空調制御装置40が、暖房用膨張弁14の絞り開度を第2モード時よりも減少させ、冷房用膨張弁16の絞り開度を第2モード時よりも増加させる。
第4モードは、除湿暖房運転モード時に、目標吹出温度TAOが第3基準温度より高くなった場合に実行される。第4モードでは、空調制御装置40が、暖房用膨張弁14の絞り開度を第3モード時よりも減少させ、冷房用膨張弁16を全開とする。
暖房運転モードでは、空調制御装置40が、暖房用膨張弁14を絞り状態とし、冷房用膨張弁16を全閉とし、暖房用開閉弁18を開き、ノズル部用開閉弁22を閉じる。従って、暖房運転モード時に構成されるサイクル構成は、特許請求の範囲に記載された非昇圧用冷媒回路に含まれる。
強暖房運転モードでは、空調制御装置40が、暖房用膨張弁14を絞り状態とし、冷房用膨張弁16を全閉とし、暖房用開閉弁18を開き、ノズル部用開閉弁22を開く。従って、本実施形態の強暖房運転モード時に構成されるサイクル構成は、特許請求の範囲に記載された昇圧用冷媒回路に含まれる。
本実施形態では、図5の全体構成図に示すように、第1実施形態の冷凍サイクル装置10に対して、バイパス通路23およびバイパス通路用開閉弁24を追加した例を説明する。なお、図5では、第1実施形態と同一もしくは均等部分には同一の符号を付している。このことは、以下の図面においても同様である。
本実施形態では、図6の全体構成図に示すように、第1実施形態の冷凍サイクル装置10に対して、冷媒回路切替手段であるノズル部用開閉弁22を廃止して、エジェクタ21のノズル部21aへ流入させる冷媒のエジェクタ側冷媒流量Gnを調整する流量調整弁25を設けた例を説明する。
本発明は上述の実施形態に限定されることなく、本発明の趣旨を逸脱しない範囲内で、以下のように種々変形可能である。
12 室内凝縮器(放熱器)
14 暖房用膨張弁
15 室外熱交換器(蒸発器)
21 エジェクタ
21a ノズル部
21d 冷媒吸引口
21f ディフューザ部
Claims (10)
- 冷媒を圧縮して吐出する圧縮機(11)と、
前記圧縮機(11)から吐出された高圧冷媒と加熱対象流体とを熱交換させて、前記高圧冷媒を放熱させる放熱器(12)と、
前記放熱器(12)から流出した冷媒を減圧させる減圧手段(14)と、
前記減圧手段(14)にて減圧された低圧冷媒と吸熱対象流体とを熱交換させて、前記低圧冷媒を蒸発させる蒸発器(15)とを備え、
さらに、前記圧縮機(11)から吐出された高圧冷媒を減圧させるノズル部(21a)から噴射される高速度の噴射冷媒の吸引作用によって、冷媒吸引口(21d)から前記蒸発器(15)下流側冷媒を吸引し、前記噴射冷媒と前記冷媒吸引口(21d)から吸引された吸引冷媒との混合冷媒を昇圧させて、前記圧縮機(11)の吸入口側へ流出させる昇圧部(21f)を有するエジェクタ(21)を備えることを特徴とする冷凍サイクル装置。 - 前記蒸発器(15)から流出した冷媒の気液を分離する気液分離手段(19)を備え、
前記気液分離手段(19)の気相冷媒流出口には、前記冷媒吸引口(21d)が接続されていることを特徴とする請求項1に記載の冷凍サイクル装置。 - 前記昇圧部(21f)にて前記混合冷媒を昇圧させる昇圧用冷媒回路と前記昇圧部(21f)にて前記混合冷媒を昇圧させない非昇圧用冷媒回路とを切り替える冷媒回路切替手段(22、24)を備えることを特徴とする請求項1または2に記載の冷凍サイクル装置。
- 前記冷媒回路切替手段は、前記ノズル部(21a)を流通する冷媒の冷媒流路を開閉する開閉手段(22)によって構成されていることを特徴とする請求項3に記載の冷凍サイクル装置。
- さらに、前記蒸発器(15)から流出した冷媒を、前記エジェクタ(21)を迂回させて前記圧縮機(11)の吸入口側へ導くバイパス通路(23)を備え、
前記冷媒回路切替手段は、前記バイパス通路(23)を開閉する開閉手段(24)によって構成されていることを特徴とする請求項3または4に記載の冷凍サイクル装置。 - 前記冷媒回路切替手段(22、24)の作動を制御する冷媒回路制御手段(40b)を備え、
前記冷媒回路制御手段(40b)は、前記圧縮機(11)の冷媒吐出能力が、予め定めた基準冷媒吐出能力以上となった際に、前記非昇圧用冷媒回路から前記昇圧用冷媒回路へ切り替えるものであることを特徴とする請求項3ないし5のいずれか1つに記載の冷凍サイクル装置。 - 前記圧縮機(11)から吐出される冷媒の流量を吐出冷媒流量(Gr)とし、前記ノズル部(21a)へ流入させる冷媒の流量をエジェクタ側冷媒流量(Gn)としたときに、
前記吐出冷媒流量(Gr)に対する前記エジェクタ側冷媒流量(Gn)の流量比(Gn/Gr)を調整する流量比調整手段(25)を備えることを特徴とする請求項1または2に記載の冷凍サイクル装置。 - 前記流量比調整手段は、前記エジェクタ側冷媒流量(Gn)を調整する流量調整弁(25)で構成されていることを特徴とする請求項7に記載の冷凍サイクル装置。
- さらに、前記放熱器へ流入させる冷媒の流量を放熱器側冷媒流量(Gc)としたときに、
前記流量比調整手段(25)の作動を制御する流量比制御手段(40c)を備え、
前記流量比制御手段(40c)は、実際の前記放熱器側冷媒流量(Gc)が、前記流量比(Gn/Gr)が0となっている際の前記放熱器側冷媒流量(Gc)以上となるように、前記流量比調整手段(25)の作動を制御するものであることを特徴とする請求項7または8に記載の冷凍サイクル装置。 - 前記流量比制御手段(40c)は、前記放熱器側冷媒流量(Gc)が極大値に近づくように、前記流量比調整手段(25)の作動を制御するものであることを特徴とする請求項9載の冷凍サイクル装置。
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CN201480051006.XA CN105556218B (zh) | 2013-10-08 | 2014-09-22 | 制冷循环装置 |
US15/027,120 US10131203B2 (en) | 2013-10-08 | 2014-09-22 | Refrigeration cycle device |
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