JP2016125774A - Refrigeration cycle device - Google Patents
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- JP2016125774A JP2016125774A JP2015000539A JP2015000539A JP2016125774A JP 2016125774 A JP2016125774 A JP 2016125774A JP 2015000539 A JP2015000539 A JP 2015000539A JP 2015000539 A JP2015000539 A JP 2015000539A JP 2016125774 A JP2016125774 A JP 2016125774A
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Abstract
Description
本発明は２つの凝縮器が一体化された一体型熱交換器を備えた冷凍サイクル装置に関するものである。 The present invention relates to a refrigeration cycle apparatus including an integrated heat exchanger in which two condensers are integrated.
冷凍冷蔵庫として構成された冷凍サイクル装置には、冷凍室と冷蔵室をそれぞれ別々の独立した冷凍サイクル回路により冷却するようにしたものがある。 Some refrigeration cycle apparatuses configured as refrigerator-freezers are configured such that the freezer compartment and the refrigerator compartment are each cooled by separate independent refrigeration cycle circuits.
このような２つの冷凍サイクル回路を有した冷凍サイクル装置では、特許文献１に示されるように各冷凍サイクル回路が具備する凝縮器を一体化して一体型熱交換器として構成することがある。 In such a refrigeration cycle apparatus having two refrigeration cycle circuits, as shown in Patent Document 1, the condensers included in each refrigeration cycle circuit may be integrated to form an integrated heat exchanger.
特許文献１に示される一体型熱交換器は、冷凍室を冷却する第１の冷媒が流される複数の第１の扁平熱交換管と、冷蔵室を冷却する第２の冷媒が流される複数の第２の扁平熱交換管が交互に上下方向に積層されたものである。また、各扁平熱交換管の間に水平方向に空気流が通過できるようにフィンが設けられている。さらに、この一体型熱交換器は各扁平熱交換管に冷媒を導入するためのヘッダと、このヘッダと各扁平熱交換を接続する複数の分岐管を備えており、各分岐管はヘッダ及び各扁平熱交換に対してろう付けされている。 The integrated heat exchanger disclosed in Patent Document 1 includes a plurality of first flat heat exchange tubes through which a first refrigerant that cools the freezer compartment and a plurality of second refrigerants through which the second refrigerant that cools the refrigerator compartment flows. The second flat heat exchange tubes are alternately stacked in the vertical direction. Further, fins are provided between the flat heat exchange tubes so that an air flow can pass in the horizontal direction. Further, the integrated heat exchanger includes a header for introducing a refrigerant into each flat heat exchange pipe, and a plurality of branch pipes connecting the header and each flat heat exchange. Brazed against flat heat exchange.
また、特許文献２にはカーエアコンの凝縮器とラジエータを一体化し、冷媒と冷却水がそれぞれ独立に流れるように第１の熱交換管と第２の熱交換管を設けた一体型熱交換器が示されている。 Patent Document 2 discloses an integrated heat exchanger in which a condenser and a radiator of a car air conditioner are integrated, and a first heat exchange pipe and a second heat exchange pipe are provided so that refrigerant and cooling water flow independently of each other. It is shown.
ところで、特許文献１及び２の一体型熱交換器では、第１の熱交換管と第２の熱交換管に同時に冷媒又は冷却水を流ように構成されている。 By the way, in the integrated heat exchanger of patent document 1 and 2, it is comprised so that a refrigerant | coolant or cooling water may be simultaneously flowed into a 1st heat exchange pipe | tube and a 2nd heat exchange pipe | tube.
しかしながら、本願発明者らが鋭意検討を行ったところ、このように第１の熱交換管と第２の熱交換管に同時に冷媒又は冷却水が流されると実は一体型熱交換器が発揮し得る熱交換効率を十分に達成できていないことを初めて見出した。 However, as a result of extensive studies by the inventors of the present application, when the refrigerant or the cooling water is caused to flow through the first heat exchange pipe and the second heat exchange pipe at the same time, the integrated heat exchanger can actually exhibit. It was found for the first time that the heat exchange efficiency could not be sufficiently achieved.
そこで、本発明は上述したような問題を鑑みてなされたものであり、一体型熱交換器を用いて従来よりも各冷凍サイクル回路における熱交換効率を向上させることができる冷凍サイクル装置を提供することを目的とする。 Therefore, the present invention has been made in view of the above-described problems, and provides a refrigeration cycle apparatus capable of improving the heat exchange efficiency in each refrigeration cycle circuit as compared with the conventional one using an integrated heat exchanger. For the purpose.
すなわち、第１の冷媒が循環する第１の冷凍サイクル回路と、第２の冷媒が循環する第２の冷凍サイクル回路と、前記第１の冷凍サイクル回路、及び、前記第２の冷凍サイクル回路を制御する運転制御部とを備えた冷凍サイクル装置であって、前記第１の冷凍サイクル回路が具備する第１の凝縮器と、前記第２の冷凍サイクル回路が具備する第２の凝縮器とが一体化された一体型熱交換器を備え、前記一体型熱交換器が、前記第１の冷媒が流されるものであり、列方向に対して並べて設けられた複数の第１の熱交換管と、前記第２の冷媒が流されるものであり、前記複数の第１の熱交換管に対してそれぞれ行方向に並列に設けられた複数の第２の熱交換管と、前記第１の熱交換管と前記第２の熱交換管の両方に接触するように設けられた複数のコルゲートフィンと、を具備し、前記運転制御部が、前記第１の熱交換管に前記第１の冷媒を流す場合には前記第２の熱交換管に前記第２の冷媒が流れないようにするとともに、前記第２の熱交換管に前記第２の冷媒を流す場合には前記第１の熱交換管に前記第１の冷媒が流れないように前記第１の冷凍サイクル回路、及び、前記第２の冷凍サイクル回路を制御することを特徴とする。 That is, a first refrigeration cycle circuit in which a first refrigerant circulates, a second refrigeration cycle circuit in which a second refrigerant circulates, the first refrigeration cycle circuit, and the second refrigeration cycle circuit A refrigeration cycle apparatus including an operation control unit for controlling, wherein a first condenser included in the first refrigeration cycle circuit and a second condenser included in the second refrigeration cycle circuit are provided. A plurality of first heat exchange tubes provided side by side with respect to the column direction, wherein the first heat exchanger flows through the integrated heat exchanger. The second refrigerant is flowed, and the plurality of second heat exchange tubes provided in parallel in the row direction with respect to the plurality of first heat exchange tubes, and the first heat exchange. A plurality of pipes provided in contact with both the pipe and the second heat exchange pipe A corrugated fin, and when the operation control unit flows the first refrigerant through the first heat exchange pipe, the second refrigerant does not flow through the second heat exchange pipe. And when flowing the second refrigerant through the second heat exchange tube, the first refrigeration cycle circuit, and the first refrigerant circuit so that the first refrigerant does not flow through the first heat exchange tube, and The second refrigeration cycle circuit is controlled.
このようなものであれば、前記一体型熱交換器には第１の冷媒と第２の冷媒のいずれか一方のみが流れているようにしているので、第１の凝縮器と第２の凝縮器の熱交換量の低下を抑えることができる。 In such a case, since only one of the first refrigerant and the second refrigerant flows through the integrated heat exchanger, the first condenser and the second condenser are used. It is possible to suppress a decrease in the heat exchange amount of the vessel.
さらに、前記コルゲートフィンは前記第１の熱交換管と前記第２の熱交換管と接触するように設けられているので、例えば前記第１の熱交換管に第１の冷媒が流れている場合には、前記コルゲートフィンにおいて前記第１の熱交換管と接触している近傍だけでなく、第２の冷媒が流れていない前記第２の熱交換管の近傍部分でも第１の冷媒は空気流に対して熱交換を行うことができる。 Further, since the corrugated fin is provided so as to contact the first heat exchange pipe and the second heat exchange pipe, for example, when the first refrigerant flows through the first heat exchange pipe In the corrugated fin, not only the vicinity of the second heat exchange pipe where the second refrigerant is not flowing, but also the vicinity of the second heat exchange pipe where the second refrigerant does not flow is the air flow. Heat exchange can be performed.
つまり、第１の冷媒と第２の冷媒が前記一体型熱交換器に対して交互に流れるように構成されているので、各冷媒と空気流との間での熱交換が行われるコルゲートフィンの放熱面積を略２倍程度に大きくすることができ、前記一体型熱交換器における熱交換効率を従来よりも向上させることができる。 That is, since the first refrigerant and the second refrigerant are configured to flow alternately with respect to the integrated heat exchanger, the corrugated fins that perform heat exchange between each refrigerant and the air flow are configured. The heat dissipating area can be increased approximately twice, and the heat exchange efficiency in the integrated heat exchanger can be improved as compared with the conventional case.
なお、上述した説明では前記一体型熱交換器において第１の冷媒のみが流れている場合を例として説明したが、この効果は前記一体型熱交換器において第２の冷媒のみが流れている場合でも同様に奏し得る。 In the above description, the case where only the first refrigerant flows in the integrated heat exchanger has been described as an example, but this effect is obtained when only the second refrigerant flows in the integrated heat exchanger. But you can play it as well.
前記一体型熱交換器では、空気流の入口側と出口側とで熱交換量を比較した場合、入口側の方が熱交換量は大きくなる傾向があることを本願発明者らは見出した。この特徴を生かしつつ、冷凍サイクル装置全体として効率よく運転できるようにするには、前記第１の冷凍サイクル回路が具備する第１の圧縮機の容量が、前記第２の冷凍サイクル回路が具備する第２の圧縮機の容量よりも大きいものであり、前記第１の熱交換管が、前記一体型熱交換器を通過する空気の流れに対して入口側に設けられており、前記第２の熱交換管が、前記一体型熱交換器を通過する空気の流れに対して出口側に設けられていればよい。 The inventors of the present invention have found that in the integrated heat exchanger, when the heat exchange amount is compared between the inlet side and the outlet side of the air flow, the heat exchange amount tends to be larger on the inlet side. In order to enable efficient operation of the entire refrigeration cycle apparatus while taking advantage of this feature, the capacity of the first compressor included in the first refrigeration cycle circuit is included in the second refrigeration cycle circuit. The capacity of the second compressor is larger, the first heat exchange pipe is provided on the inlet side with respect to the flow of air passing through the integrated heat exchanger, The heat exchange pipe should just be provided in the exit side with respect to the flow of the air which passes the said integrated heat exchanger.
コルゲートフィンだけでなく、冷媒が流れていない熱交換管の表面積も放熱面積として利用できるようにし、さらに熱交換効率を向上させるには、前記第１の熱交換管と前記第２の熱交換管との間を接続する接続部をさらに備えたものであればよい。 In order to make it possible to use not only the corrugated fins but also the surface area of the heat exchange pipe where the refrigerant does not flow as the heat radiation area and further improve the heat exchange efficiency, the first heat exchange pipe and the second heat exchange pipe What is necessary is just to further provide the connection part which connects between.
前記一体型熱交換器を簡単な構成とするには、前記第１の熱交換管及び前記第２の第２の熱交換管と、前記コルゲートフィンが列方向に対して交互に積層されているものであればよい。 In order to make the integrated heat exchanger simple, the first heat exchange pipe, the second second heat exchange pipe, and the corrugated fins are alternately stacked in the column direction. Anything is acceptable.
例えば特許文献１に記載の一体型熱交換器のようにろう付け箇所が多数になることにより、組立性が悪くなり製造コストが上昇するのを防ぐことができるようにするには、前記第１の熱交換管の端部と、前記第２の熱交換管の端部が挿入される中空のヘッダをさらに備え、前記ヘッダが、前記第１の冷媒と第２の冷媒が混じらないように内部を仕切る仕切り部材を具備するものであればよい。 For example, in order to prevent an increase in manufacturing cost due to a large number of brazing points as in the integrated heat exchanger described in Patent Document 1, it is possible to prevent the above-described first. And a hollow header into which the end of the second heat exchange tube is inserted, and the header is arranged so that the first refrigerant and the second refrigerant are not mixed with each other. What is necessary is just to comprise the partition member which partitions off.
本発明の冷凍サイクル装置を例えば冷凍冷蔵庫として構成した場合に熱交換量から考えた好ましい実施の態様としては、前記第１の冷凍サイクル回路が具備する第１の蒸発器は、冷凍室を冷却するように構成されており、前記第２の冷凍サイクル回路が具備する第２の蒸発器は、冷蔵室を冷却するように構成されているものが挙げられる。 For example, when the refrigeration cycle apparatus of the present invention is configured as a refrigeration refrigerator, the first evaporator included in the first refrigeration cycle circuit cools the freezer compartment. The second evaporator provided in the second refrigeration cycle circuit is configured to cool the refrigerator compartment.
前記運転制御部による各冷凍サイクル回路の具体的な制御態様としては、前記運転制御部が、前記冷凍室又は前記冷蔵室が交互に冷却されるように前記第１の冷凍サイクル回路及び前記第２の冷凍サイクル回路を制御するように構成されているものが挙げられる。 As a specific control mode of each refrigeration cycle circuit by the operation control unit, the operation control unit includes the first refrigeration cycle circuit and the second refrigeration cycle so that the freezer compartment or the refrigerator compartment is alternately cooled. Are configured to control the refrigeration cycle circuit.
このように本発明の冷凍サイクル装置によれば、一体型熱交換器に対して交互に第１の冷媒と第２の冷媒が流されるように構成されているので、コルゲートフィンにおいて冷媒が流れていない熱交換管に接触している部分についても流れている冷媒の放熱のために利用することができ、従来よりも放熱面積が大きくなることにより熱交換効率を向上させることができる。 As described above, according to the refrigeration cycle apparatus of the present invention, the first refrigerant and the second refrigerant are alternately flowed to the integrated heat exchanger, so that the refrigerant flows in the corrugated fins. The portion in contact with the heat exchange pipe that is not present can be used for heat dissipation of the flowing refrigerant, and the heat exchange efficiency can be improved by increasing the heat dissipation area as compared with the conventional case.
本発明の一実施形態に係る冷凍サイクル装置について図１乃至９を参照しながら説明する。 A refrigeration cycle apparatus according to an embodiment of the present invention will be described with reference to FIGS.
本実施形態の冷凍サイクル装置は図１に示すように２つの独立した第１の冷凍サイクル回路１０１と、第２の冷凍サイクル回路１０２と、第１の冷凍サイクル回路１０１と第２の冷凍サイクル回路１０２の動作を制御する運転制御部８と、を備えた冷凍冷蔵庫２００である。 As shown in FIG. 1, the refrigeration cycle apparatus of the present embodiment includes two independent first refrigeration cycle circuits 101, a second refrigeration cycle circuit 102, a first refrigeration cycle circuit 101, and a second refrigeration cycle circuit. It is the refrigerator-freezer 200 provided with the operation control part 8 which controls operation | movement of 102.
前記第１の冷凍サイクル回路１０１は、冷凍室を冷却するために用いられるものであって、第１の圧縮機１１、第１の凝縮器１２、第１の絞り１３、第１の蒸発器１４の順番で第１の冷媒が循環するように構成してある。すなわち、前記第１の蒸発器１４は冷凍室内を冷却するように構成してある。 The first refrigeration cycle circuit 101 is used for cooling the freezer compartment, and includes a first compressor 11, a first condenser 12, a first throttle 13, and a first evaporator 14. The first refrigerant is circulated in this order. That is, the first evaporator 14 is configured to cool the inside of the freezer compartment.
前記第２の冷凍サイクル回路１０２は、冷蔵室を冷却するために用いられるものであって、第２の圧縮機２１、第２の凝縮器２２、第２の絞り２３、第２の蒸発器２４の順番で第２の冷媒が循環するように構成してある。すなわち、前記第２の蒸発器２４は冷蔵室内を冷却するように構成してある。 The second refrigeration cycle circuit 102 is used for cooling the refrigerating chamber, and includes a second compressor 21, a second condenser 22, a second throttle 23, and a second evaporator 24. The second refrigerant circulates in this order. That is, the second evaporator 24 is configured to cool the refrigerator compartment.
前記第１の冷凍サイクル回路１０１は冷蔵室よりも低い温度に保つ必要のある冷凍室を冷却するためのものであるので、前記第１の圧縮機１１は前記第２の圧縮機２１よりも容量の大きいものにしてある。 Since the first refrigeration cycle circuit 101 is for cooling a freezing room that needs to be maintained at a temperature lower than that of the refrigerating room, the first compressor 11 has a capacity larger than that of the second compressor 21. It's big.
また、前記第１の凝縮器１２と前記第２の凝縮器２２は一体化してあり、図２に示す一体型熱交換器１００を構成している。 Moreover, the said 1st condenser 12 and the said 2nd condenser 22 are integrated, and comprise the integrated heat exchanger 100 shown in FIG.
前記一体型熱交換器１００は、扁平板状で内部に冷媒が流される扁平冷媒管３と、波型に成型されたコルゲートフィン４と、前記扁平冷媒管３の両端にそれぞれ取り付けられた２つのヘッダ５１、５２からなるヘッダ機構とを備えたものである。前記扁平冷媒管３と前記コルゲートフィン４は図３に示すように交互に上下方向（列方向）に積層してあり、図示しないファンにより形成される空気流が水平方向（行方向）に通過できるように構成してある。本実施形態では紙面奥側から手前側へ空気流が通過するように構成してある。 The integrated heat exchanger 100 includes a flat refrigerant pipe 3 that is flat and into which a refrigerant flows, corrugated fins 4 that are formed in a corrugated shape, and two attached to both ends of the flat refrigerant pipe 3. And a header mechanism composed of headers 51 and 52. The flat refrigerant tubes 3 and the corrugated fins 4 are alternately stacked in the vertical direction (column direction) as shown in FIG. 3, and an air flow formed by a fan (not shown) can pass in the horizontal direction (row direction). It is constituted as follows. In this embodiment, it is comprised so that an airflow may pass from the paper surface back side to this side.
前記扁平冷媒管３は、図３及び図４に示すように第１の冷媒が流される第１の熱交換管３１と、前記第１の熱交換管３１に対して並列に設けられ、第２の冷媒が流される第２の熱交換管３２と、前記第１の熱交換管３１と前記第２の熱交換管３２との間を接続する接続部３３と、を備えたものである。 As shown in FIGS. 3 and 4, the flat refrigerant pipe 3 is provided in parallel to the first heat exchange pipe 31 through which the first refrigerant flows and the first heat exchange pipe 31. The second heat exchange pipe 32 through which the refrigerant flows is provided, and a connection portion 33 that connects between the first heat exchange pipe 31 and the second heat exchange pipe 32.
前記第１の熱交換管３１及び前記第２の熱交換管３２は、図４に示すように複数の小管が水平方向に一列に並べて設けてある扁平多穴管である。すなわち、前記一体型熱交換器１００は、マイクロチャネル型熱交換器として構成してある。前記第１の熱交換管３１に注目した場合、複数の第１の熱交換管３１は上下方向（列方向）に対して前記コルゲートフィン４が設けられるように等間隔で離間させて並べて設けてある。前記第２の熱交換管３２に注目した場合も同様で、複数の第２の熱交換管３２も上下方向に等間隔で並べて設けてある。また、各第２の熱交換管３２は各第１の熱交換管３１と水平方向に同じ高さで対になるように設けてある。 The first heat exchange tube 31 and the second heat exchange tube 32 are flat multi-hole tubes in which a plurality of small tubes are arranged in a row in the horizontal direction as shown in FIG. That is, the integrated heat exchanger 100 is configured as a microchannel heat exchanger. When attention is paid to the first heat exchange pipe 31, a plurality of first heat exchange pipes 31 are arranged side by side at equal intervals so that the corrugated fins 4 are provided in the vertical direction (column direction). is there. The same applies to the case where attention is paid to the second heat exchange pipe 32, and a plurality of second heat exchange pipes 32 are also arranged at equal intervals in the vertical direction. Each second heat exchange tube 32 is provided to be paired with each first heat exchange tube 31 at the same height in the horizontal direction.
前記接続部３３は、図４に示すように一対の第１の熱交換管３１と第２の熱交換管３２を接続するものであり、この接続部３３を介して双方の熱伝導を可能とするとともに、第１の熱交換管３１と第２の熱交換管３２を一体化している。このため、前記扁平冷媒管３は概略板状とすることができ、組立時に扁平冷媒管３とコルゲートフィン４を積層していく際の工数を低減することができる。 As shown in FIG. 4, the connecting portion 33 connects a pair of the first heat exchange pipe 31 and the second heat exchange pipe 32, and enables heat conduction through the connecting portion 33. In addition, the first heat exchange pipe 31 and the second heat exchange pipe 32 are integrated. For this reason, the said flat refrigerant | coolant pipe | tube 3 can be made into a substantially plate shape, and the man-hour at the time of laminating | stacking the flat refrigerant | coolant pipe | tube 3 and the corrugated fin 4 at the time of an assembly can be reduced.
前記コルゲートフィン４は、図２及び図３に示すように側面側から見た場合に三角波状をなすようにアルミの板材を曲げ加工したものであり、その頂点部分の稜線が前記扁平冷媒管３に対してろう付けしてある。 The corrugated fin 4 is formed by bending an aluminum plate so as to form a triangular wave when viewed from the side as shown in FIGS. 2 and 3, and the ridge line of the apex portion thereof is the flat refrigerant tube 3. It is brazed against.
前記ヘッダ機構は、冷媒の導出入が行われる導出入側ヘッダ５１と、前記扁平冷媒管３を通過した冷媒を折り返して再び前記扁平冷媒管３へ戻す折り返し側ヘッダ５２とを備えている。 The header mechanism includes a lead-in / out-side header 51 where the refrigerant is led out / in, and a folded-back header 52 that folds back the refrigerant that has passed through the flat refrigerant pipe 3 and returns the refrigerant to the flat refrigerant pipe 3 again.
前記導出入側ヘッダ５１は、図２及び図５に示すように上下方向に延びる概略直方体状の中空の筐体であって、内部に上下方向に延び第１の冷媒と第２の冷媒が混じらないように仕切る仕切り部材５１１を備えている。 As shown in FIGS. 2 and 5, the lead-in header 51 is a hollow housing having a substantially rectangular parallelepiped shape extending in the vertical direction, and extends in the vertical direction to mix the first refrigerant and the second refrigerant. A partition member 511 for partitioning is provided.
また、前記導出入側ヘッダ５１は、中央部で水平方向にも仕切られており（図示しない）、第１の冷媒導入室、第１の冷媒導出室、第２の冷媒導入室、第２の冷媒導出室からなる計４つの部屋が形成されている。 The lead-in / out-side header 51 is also horizontally partitioned at the center (not shown), and includes a first refrigerant introduction chamber, a first refrigerant lead-out chamber, a second refrigerant introduction chamber, and a second refrigerant introduction chamber. There are a total of four chambers consisting of refrigerant outlet chambers.
前記第１の冷媒導入室は、第１の圧縮機１１から第１の冷媒が導入される第１の導入ポート６１と連通するとともに、導入された第１の冷媒が複数の第１の熱交換管３１に分配されるように構成してある。前記第１の冷媒導出室は、前記折り返し側ヘッダ５２を経由して戻ってきた第１の冷媒を前記第１の絞り１３へと導出するための第１の導出ポート７１と連通させてある。 The first refrigerant introduction chamber communicates with a first introduction port 61 into which the first refrigerant is introduced from the first compressor 11, and the introduced first refrigerant has a plurality of first heat exchanges. It is configured to be distributed to the pipe 31. The first refrigerant lead-out chamber communicates with a first lead-out port 71 for leading the first refrigerant returned through the turn-up-side header 52 to the first throttle 13.
また、前記第２の冷媒導入室は第２の導入ポート６２と連通しており、前記第２の冷媒導出室は第２の導出ポート７２と連通しており、その構造は第１の導入室及び第１の導出室と同様にしてある。 Further, the second refrigerant introduction chamber communicates with the second introduction port 62, the second refrigerant lead-out chamber communicates with the second lead-out port 72, and the structure thereof is the first introduction chamber. The same as the first lead-out chamber.
図５に示すように前記第１の熱交換管３１及び前記第２の熱交換管３２の端部は前記導出入側ヘッダ５１の内部空間内へ突出するように差し込んである。したがって、前記導入側ヘッダと前記熱交換管との間を接続する例えば分岐管等を設ける必要がなく、ろう付け箇所を少なくし、組立性を良くすることができる。 As shown in FIG. 5, the end portions of the first heat exchange pipe 31 and the second heat exchange pipe 32 are inserted so as to protrude into the inner space of the lead-out inlet header 51. Therefore, it is not necessary to provide, for example, a branch pipe or the like for connecting between the introduction side header and the heat exchange pipe, and the number of brazed portions can be reduced and the assemblability can be improved.
前記運転制御部８は、ＣＰＵ、メモリ、Ａ／Ｄ・Ｄ／Ａコンバータ、入出力手段等を備えたいわゆるコンピュータであって、前記メモリに格納されている冷凍サイクル装置用プログラムが実行されることによりその機能が実現されるものである。 The operation control unit 8 is a so-called computer including a CPU, a memory, an A / D / D / A converter, an input / output means, and the like, and the program for the refrigeration cycle apparatus stored in the memory is executed. The function is realized by.
すなわち、前記運転制御部８は、前記第１の熱交換管３１に前記第１の冷媒を流す場合には前記第２の熱交換管３２に前記第２の冷媒が流れないようにするとともに、前記第２の熱交換管３２に前記第２の冷媒を流す場合には前記第１の熱交換管３１に前記第１の冷媒が流れないように前記第１の冷凍サイクル回路１０１、及び、前記第２の冷凍サイクル回路１０２を制御するように構成してある。 That is, the operation control unit 8 prevents the second refrigerant from flowing into the second heat exchange pipe 32 when the first refrigerant flows through the first heat exchange pipe 31. When flowing the second refrigerant through the second heat exchange pipe 32, the first refrigeration cycle circuit 101, and the first refrigerant circuit 101 so that the first refrigerant does not flow through the first heat exchange pipe 31; The second refrigeration cycle circuit 102 is configured to be controlled.
より具体的には、前記運転制御部８は少なくとも前記第１の圧縮機１１と前記第２の圧縮機２１をオンオフ制御するものであり、前記第１の圧縮機１１が駆動している間は前記第２の圧縮機２１を停止させ、前記第２の圧縮機２１が駆動している間は前記第１の圧縮機１１を停止させるように構成してある。つまり、前記運転制御部８は第１の圧縮機１１と第２の圧縮機２１を交互に運転させるようにしてある。 More specifically, the operation control unit 8 controls on / off of at least the first compressor 11 and the second compressor 21, and while the first compressor 11 is being driven. The second compressor 21 is stopped, and the first compressor 11 is stopped while the second compressor 21 is driven. That is, the operation control unit 8 operates the first compressor 11 and the second compressor 21 alternately.
このように第１の圧縮機１１と第２の圧縮機２１が交互にオン状態となるように制御している場合の冷凍室及び冷蔵室の温度変化と、前記一体型熱交換器１００の入口側と出口側の冷媒の温度を図６に示す。 Thus, the temperature change of the freezer compartment and the refrigerator compartment when the first compressor 11 and the second compressor 21 are controlled to be alternately turned on, and the inlet of the integrated heat exchanger 100 FIG. 6 shows the temperature of the refrigerant on the side and the outlet side.
前記第１の圧縮機１１と前記第２の圧縮機２１が交互に運転されるので、図６に示すように冷凍室の温度と冷蔵室の温度は最高温度と最低温度の間を周期的に変化することになる。また、冷凍室の温度変化と冷蔵室の温度変化の位相はほぼ半周期ずれた状態となる。加えて、前記一体型熱交換器１００の入口出口の温度も冷凍室、冷蔵室の温度とほぼ同じ周期で変化することになる。より具体的には、前記第１の圧縮機１１がオン状態であり、前記第２の圧縮機２１がＯＦＦ状態の間は、第１の冷媒には入口側と出口側で大きな温度差が生じ、凝縮による温度低下が生じていることが分かる。一方、第２の冷媒では第２の圧縮機２１による圧縮が行われず入口側の温度は上昇しない。前記第１の圧縮機１１がＯＦＦ状態であり、前記第２の圧縮機２１がオン状態の間はこの温度関係が逆転することになる。 Since the first compressor 11 and the second compressor 21 are operated alternately, the temperature of the freezer compartment and the temperature of the refrigerator compartment are periodically between the highest temperature and the lowest temperature as shown in FIG. Will change. Moreover, the phase of the temperature change of a freezer compartment and the temperature change of a refrigerator compartment will be in the state which shifted | deviated substantially half a cycle. In addition, the temperature at the inlet / outlet of the integrated heat exchanger 100 also changes at substantially the same cycle as the temperatures of the freezer compartment and the refrigerator compartment. More specifically, when the first compressor 11 is on and the second compressor 21 is off, the first refrigerant has a large temperature difference between the inlet side and the outlet side. It can be seen that a temperature decrease due to condensation occurs. On the other hand, the second refrigerant is not compressed by the second compressor 21 and the temperature on the inlet side does not rise. This temperature relationship is reversed while the first compressor 11 is in the OFF state and the second compressor 21 is in the ON state.
このように構成された冷凍サイクル装置による熱交換量及び熱交換効率の向上に関する効果について実験結果に基づいて説明する。 The effect regarding the improvement of the heat exchange amount and heat exchange efficiency by the refrigeration cycle apparatus configured as described above will be described based on experimental results.
実験として以下の３つの条件で前記一体型熱交換器に温水を流し、空気流との間の熱交換量の測定を行った。 As an experiment, warm water was passed through the integrated heat exchanger under the following three conditions, and the amount of heat exchange with the air stream was measured.
条件１：前記一体型熱交換器１００全体の性能を把握するために、前記第１の導入ポート６１と前記第２の導出ポート７２を配管で接続し、前記第２の導入ポート６２から温水を導入した場合の空気流との間の熱交換量を測定した。すなわち、図７に示すように冷媒は第２の導入ポート６２、第２の熱交換管３２寛、第２の導出ポート７２、第１の導入ポート６１、第１の熱交換管３１、第１の導出ポート７１の順番で温水が循環することになる。 Condition 1: In order to grasp the overall performance of the integrated heat exchanger 100, the first inlet port 61 and the second outlet port 72 are connected by piping, and hot water is supplied from the second inlet port 62. The amount of heat exchange with the air flow when introduced was measured. That is, as shown in FIG. 7, the refrigerant includes the second introduction port 62, the second heat exchange pipe 32, the second outlet port 72, the first introduction port 61, the first heat exchange pipe 31, the first The hot water circulates in the order of the outlet ports 71.
条件２：本実施形態の運転制御部８による制御と同様の状態が模擬されるように第１の熱交換管３１にのみ温水が流れている状態で第１の凝縮器１２における熱交換量を測定し、第２の熱交換管３２にのみが温水が流れている状態で第２の凝縮器２２における熱交換量をそれぞれ測定した。より具体的には、図８（ａ）に示すように空気入口側の第１の凝縮器１２のみを運転した状態での熱交換量と、図８（ｂ）に示すように空気出口側の第２の凝縮器２２のみを運転した状態での熱交換量を測定した。 Condition 2: The amount of heat exchange in the first condenser 12 is set in a state in which hot water flows only through the first heat exchange pipe 31 so that the same state as the control by the operation control unit 8 of the present embodiment is simulated. The amount of heat exchange in the second condenser 22 was measured with warm water flowing only through the second heat exchange pipe 32. More specifically, the heat exchange amount when only the first condenser 12 on the air inlet side is operated as shown in FIG. 8 (a), and the air outlet side as shown in FIG. 8 (b). The heat exchange amount in a state where only the second condenser 22 was operated was measured.
条件３：図９に示すように第１の冷媒と第２の冷媒をそれぞれ同時に前記一体型熱交換器１００に導入され流れている状態を模擬するように、第１の熱交換管３１と第２の熱交換３２の同時に並列させて温水を流し、第１の凝縮器１２での熱交換量と第２の凝縮器２２での熱交換量を測定した。 Condition 3: As shown in FIG. 9, the first heat exchange pipe 31 and the second refrigerant are simulated so that the first refrigerant and the second refrigerant are simultaneously introduced into the integrated heat exchanger 100 and flowed. The two heat exchanges 32 were simultaneously arranged in parallel and hot water was allowed to flow, and the heat exchange amount in the first condenser 12 and the heat exchange amount in the second condenser 22 were measured.
熱交換量の測定では、対応する導入ポート及び導出ポートにおける冷媒の温度を測定し、その温度低下量から空気との間で熱交換された熱交換量を算出している。
実験の結果は以下の表のようになった。
In the measurement of the amount of heat exchange, the temperature of the refrigerant at the corresponding introduction port and outlet port is measured, and the amount of heat exchange exchanged with air is calculated from the amount of temperature decrease.
The results of the experiment are shown in the following table.
条件１での測定では条件２での測定と比較して温水が２倍の距離を流れているため、もし本実施形態の冷凍サイクル装置による効果がない場合には、条件２での測定結果はそれぞれ条件１の測定結果の略半分になるはずである。 In the measurement under the condition 1, since the hot water flows twice as much as the measurement under the condition 2, if there is no effect by the refrigeration cycle apparatus of the present embodiment, the measurement result under the condition 2 is Each should be approximately half of the measurement result of condition 1.
ところが、条件１の測定結果と条件２の測定結果を比較すると、空気流の入口側に位置する第１の凝縮器１２における熱交換量は、条件１の測定結果を上回るとともに、空気流の出口側に位置する第２の凝縮器２２における熱交換量も条件１の８５％を達成できている。 However, when the measurement result of condition 1 and the measurement result of condition 2 are compared, the heat exchange amount in the first condenser 12 located on the inlet side of the air flow exceeds the measurement result of condition 1, and the outlet of the air flow The amount of heat exchange in the second condenser 22 located on the side can also achieve 85% of the condition 1.
この結果から本実施形態の冷凍サイクル装置であれば、放熱時間、放熱距離が短くなっているにもかかわらず、第１の凝縮器１２、第２の凝縮器２２のいずれにおいても放熱能力を向上させられることが分かる。 From this result, in the refrigeration cycle apparatus of the present embodiment, the heat dissipating capability is improved in both the first condenser 12 and the second condenser 22 even though the heat dissipating time and the heat dissipating distance are shortened. You can see that
このような結果となるのは、例えば図８（ａ）に示すように前記一体型熱交換器１００において第１の冷媒のみが流れ、第２の冷媒が流れていない場合を考えると以下のような現象が生じているためであると考えられる。すなわち、第２の冷媒が流れておらず、第１の冷媒と比較して低温で保たれているので、第１の冷媒は第１の熱交換管３１とコルゲートフィン４において第１の熱交換管３１と接触している部分の周囲のみだけでなく、第２の熱交換管３２及びコルゲートフィン４において第２の熱交換管３２と接触している部分の周囲でも放熱が行える。したがって凝縮器１２単体で構成した場合でよりも放熱面積を大きくすることができるので、熱交換効率を高められると考えられる。 Considering the case where only the first refrigerant flows and the second refrigerant does not flow in the integrated heat exchanger 100, for example, as shown in FIG. This is thought to be due to the occurrence of various phenomena. That is, since the second refrigerant does not flow and is kept at a low temperature compared to the first refrigerant, the first refrigerant exchanges the first heat in the first heat exchange pipe 31 and the corrugated fin 4. The heat can be radiated not only around the part in contact with the pipe 31 but also around the part in contact with the second heat exchange pipe 32 in the second heat exchange pipe 32 and the corrugated fin 4. Therefore, since the heat radiation area can be increased as compared with the case of the condenser 12 alone, it is considered that the heat exchange efficiency can be improved.
一方、条件３のように第１の熱交換管３１と第２の熱交換管３２にそれぞれ第１の冷媒と第２の冷媒を同時に流すと、各冷媒の入口温度が高温で略同じとなるため、上述したような熱伝導が生じにくく、前記一体型の熱交換器の略半分ずつで熱交換が起こることになる。したがって、条件２と比較して条件３の場合には熱交換量が低下してしまう。 On the other hand, when the first refrigerant and the second refrigerant are caused to flow simultaneously through the first heat exchange pipe 31 and the second heat exchange pipe 32 as in Condition 3, the inlet temperatures of the respective refrigerants are substantially the same at high temperatures. Therefore, heat conduction as described above is unlikely to occur, and heat exchange occurs in approximately half of the integrated heat exchanger. Therefore, in the case of condition 3 as compared with condition 2, the amount of heat exchange is reduced.
これらのことから、本実施形態の冷凍冷蔵庫２００では、前記コルゲートフィン４が前記第１の熱交換管３１、前記第２の熱交換管３２の両方に接触するように取り付けていること、前記第１の熱交換管３１と前記第２の熱交換管３２の接続部３３で連結されていること、さらに、前記運転制御部８が、前記一体型熱交換器１００に対して第１の冷媒、第２の冷媒を交互に流すように制御を行うことから、条件１乃至３の測定結果からも分かるように熱交換効率を大幅に向上させることができる。 From these things, in the refrigerator-freezer 200 of this embodiment, the corrugated fin 4 is attached so as to contact both the first heat exchange pipe 31 and the second heat exchange pipe 32, the first The first heat exchange pipe 31 and the second heat exchange pipe 32 are connected by a connection portion 33, and the operation control unit 8 is connected to the integrated heat exchanger 100 with a first refrigerant, Since the control is performed so that the second refrigerant flows alternately, the heat exchange efficiency can be greatly improved as can be seen from the measurement results of conditions 1 to 3.
その他の実施形態について説明する。 Other embodiments will be described.
前記実施形態では、冷凍サイクル装置として冷凍室と冷蔵室を備えた冷凍冷蔵庫を構成したが、例えば２つの冷凍室又は２つの冷蔵室をそれぞれ独立に冷却するために本発明の冷凍サイクル装置を用いても構わない。 In the said embodiment, although the freezer refrigerator provided with the freezer compartment and the refrigerator compartment was comprised as a refrigerating-cycle apparatus, for example, in order to cool two freezer compartments or two refrigerator compartments, respectively, the refrigerating-cycle apparatus of this invention is used. It doesn't matter.
前記運転制御部は、第１の圧縮機のオン状態と第２の圧縮機のオン状態が交互に表れるように制御するように構成していたが、例えば第１の圧縮機のオン状態と第２の圧縮機のオン状態が一部の期間において重複していてもよい。すなわち、時系列的にみて一部でも第１の冷凍サイクル回路又は第２の冷凍サイクル回路のいずれか一方のみが運転している状態が存在すればよい。また前記運転制御部は前記一体型熱交換器に対して第１の冷媒、第２の冷媒のいずれか一方のみが流れるように第１の圧縮機と第２の圧縮機を制御するのではなく、例えば流路に設けられるバルブの開閉や、接続配管のつなぎ方を制御することでいずれか一方の冷媒のみが前記一体型熱交換器に流入するように制御してもよい。 The operation control unit is configured to perform control so that the ON state of the first compressor and the ON state of the second compressor appear alternately. For example, the ON state of the first compressor and the ON state of the first compressor The ON state of the two compressors may overlap in some periods. That is, it is sufficient that only one of the first refrigeration cycle circuit and the second refrigeration cycle circuit is operating in part in view of time series. The operation control unit does not control the first compressor and the second compressor so that only one of the first refrigerant and the second refrigerant flows through the integrated heat exchanger. For example, it may be controlled such that only one of the refrigerants flows into the integrated heat exchanger by controlling opening and closing of a valve provided in the flow path and connection of connection pipes.
前記コルゲートフィンの形状は前記実施形態に示された三角波に限られず、矩形波等の様々な波形状をなすものであっても構わない。 The shape of the corrugated fin is not limited to the triangular wave shown in the embodiment, and may be various wave shapes such as a rectangular wave.
前記第１の熱交換管及び前記第２の熱交換は前記接続部により接続されていなくてもよい。すくなくとも第１の熱交換管と第２の熱交換の双方に前記コルゲートフィンが接触するようにしてあればよい。 The first heat exchange tube and the second heat exchange may not be connected by the connecting portion. At least the corrugated fins may be in contact with both the first heat exchange pipe and the second heat exchange.
前記実施形態では圧縮機の吐出容量の大きい第１の冷凍サイクル回路が具備する第１の凝縮器の前記一体型熱交換器において空気流の入口側に配置したが、用途によっては空気流の出口側に配置してもよい。 In the said embodiment, although it arrange | positioned in the said integrated heat exchanger of the 1st condenser with which the 1st refrigeration cycle circuit with a large discharge capacity of a compressor is equipped, it is arrange | positioned at the inlet side of the airflow depending on the use. It may be arranged on the side.
列方向と行方向は、上下方向と水平方向の組み合わせに限られるものではない。例えば列方向が水平方向であり、行方向が上下方向であっても構わない。 The column direction and the row direction are not limited to the combination of the vertical direction and the horizontal direction. For example, the column direction may be the horizontal direction and the row direction may be the vertical direction.
その他、本発明の趣旨に反しない限りにおいて、様々な実施形態の組み合わせや変形を行っても構わない。 In addition, various combinations and modifications of the embodiments may be performed without departing from the spirit of the present invention.
２００・・・冷凍冷蔵庫（冷凍サイクル装置）
１００・・・一体型熱交換器
１０１・・・第１の冷凍サイクル回路
１１ ・・・第１の圧縮機
１２ ・・・第１の凝縮器
１３ ・・・第１の絞り
１４ ・・・第１の蒸発器
１０２・・・第２の冷凍サイクル回路
２１ ・・・第２の圧縮機
２２ ・・・第２の凝縮器
２３ ・・・第２の絞り
２４ ・・・第２の蒸発器
３ ・・・扁平冷媒管
３１ ・・・第１の熱交換管
３２ ・・・第２の熱交換管
３３ ・・・接続部
４ ・・・コルゲートフィン
５１ ・・・導出入側ヘッダ
５２ ・・・折り返し側ヘッダ
６１ ・・・第１の導入ポート
６２ ・・・第２の導入ポート
７１ ・・・第１の導出ポート
７２ ・・・第２の導出ポート
８ ・・・運転制御部
200: Refrigeration refrigerator (refrigeration cycle apparatus)
DESCRIPTION OF SYMBOLS 100 ... Integrated heat exchanger 101 ... 1st refrigeration cycle circuit 11 ... 1st compressor 12 ... 1st condenser 13 ... 1st aperture 14 ... 1st 1 evaporator 102 2nd refrigeration cycle circuit 21 2nd compressor 22 2nd condenser 23 2nd throttle 24 2nd evaporator 3 ... flat refrigerant pipe 31 ... first heat exchange pipe 32 ... second heat exchange pipe 33 ... connection part 4 ... corrugated fin 51 ... lead-out inlet side header 52 ... Return side header 61 ... 1st introduction port 62 ... 2nd introduction port 71 ... 1st derivation port 72 ... 2nd derivation port 8 ... operation control part
Claims (7)
前記第１の冷凍サイクル回路が具備する第１の凝縮器と、前記第２の冷凍サイクル回路が具備する第２の凝縮器とが一体化された一体型熱交換器を備え、
前記一体型熱交換器が、
前記第１の冷媒が流されるものであり、列方向に対して並べて設けられた複数の第１の熱交換管と、
前記第２の冷媒が流されるものであり、前記複数の第１の熱交換管に対してそれぞれ行方向に並列に設けられた複数の第２の熱交換管と、
前記第１の熱交換管と前記第２の熱交換管の両方に接触するように設けられた複数のコルゲートフィンと、を具備し、
前記運転制御部が、前記第１の熱交換管に前記第１の冷媒を流す場合には前記第２の熱交換管に前記第２の冷媒が流れないようにするとともに、前記第２の熱交換管に前記第２の冷媒を流す場合には前記第１の熱交換管に前記第１の冷媒が流れないように前記第１の冷凍サイクル回路、及び、前記第２の冷凍サイクル回路を制御することを特徴とする冷凍サイクル装置。 The first refrigeration cycle circuit in which the first refrigerant circulates, the second refrigeration cycle circuit in which the second refrigerant circulates, the first refrigeration cycle circuit, and the second refrigeration cycle circuit are controlled. A refrigeration cycle apparatus comprising an operation control unit,
An integrated heat exchanger in which the first condenser included in the first refrigeration cycle circuit and the second condenser included in the second refrigeration cycle circuit are integrated;
The integrated heat exchanger is
A plurality of first heat exchange pipes arranged side by side with respect to the column direction, wherein the first refrigerant is flowed;
A plurality of second heat exchange tubes provided in parallel with each other in the row direction with respect to the plurality of first heat exchange tubes;
A plurality of corrugated fins provided in contact with both the first heat exchange pipe and the second heat exchange pipe,
When the operation control unit causes the first refrigerant to flow through the first heat exchange pipe, the second heat exchange pipe is prevented from flowing through the second heat exchange pipe and the second heat When flowing the second refrigerant through the exchange pipe, the first refrigeration cycle circuit and the second refrigeration cycle circuit are controlled so that the first refrigerant does not flow through the first heat exchange pipe. A refrigeration cycle apparatus characterized by:
前記第１の熱交換管が、前記一体型熱交換器を通過する空気の流れに対して入口側に設けられており、
前記第２の熱交換管が、前記一体型熱交換器を通過する空気の流れに対して出口側に設けられている請求項１記載の冷凍サイクル装置。 The capacity of the first compressor included in the first refrigeration cycle circuit is larger than the capacity of the second compressor included in the second refrigeration cycle circuit,
The first heat exchange pipe is provided on the inlet side with respect to a flow of air passing through the integrated heat exchanger;
The refrigeration cycle apparatus according to claim 1, wherein the second heat exchange pipe is provided on an outlet side with respect to a flow of air passing through the integrated heat exchanger.
前記ヘッダが、前記第１の冷媒と第２の冷媒が混じらないように内部を仕切る仕切り部材を具備する請求項１乃至４いずれかに記載の冷凍サイクル装置。 A hollow header into which an end of the first heat exchange tube and an end of the second heat exchange tube are inserted;
The refrigeration cycle apparatus according to any one of claims 1 to 4, wherein the header includes a partition member that partitions the interior so that the first refrigerant and the second refrigerant are not mixed.
前記第２の冷凍サイクル回路が具備する第２の蒸発器は、冷蔵室を冷却するように構成されている請求項１乃至５いずれかに記載の冷凍サイクル装置。 The first evaporator included in the first refrigeration cycle circuit is configured to cool the freezer compartment,
The refrigeration cycle apparatus according to any one of claims 1 to 5, wherein the second evaporator included in the second refrigeration cycle circuit is configured to cool the refrigerator compartment.
The said operation control part is comprised so that the said 1st freezing cycle circuit and the said 2nd freezing cycle circuit may be controlled so that the said freezer compartment or the said refrigerator compartment may be cooled alternately. Refrigeration cycle equipment.
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| Application Number | Priority Date | Filing Date | Title |
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| JP2015000539A JP2016125774A (en) | 2015-01-05 | 2015-01-05 | Refrigeration cycle device |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2015000539A JP2016125774A (en) | 2015-01-05 | 2015-01-05 | Refrigeration cycle device |
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| JP2016125774A true JP2016125774A (en) | 2016-07-11 |
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Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62171863U (en) * | 1986-03-17 | 1987-10-31 | ||
| JP2000146330A (en) * | 1998-11-04 | 2000-05-26 | Mitsubishi Heavy Ind Ltd | Air conditioner, plate fin tube type heat exchanger, drying cold storage chamber, refrigerant circuit and cooling device |
| JP2001201194A (en) * | 2000-01-18 | 2001-07-27 | Matsushita Refrig Co Ltd | Cold storage system with deep freezer |
| JP2007303777A (en) * | 2006-05-15 | 2007-11-22 | Hitachi Appliances Inc | Refrigerator |
| JP2010243055A (en) * | 2009-04-06 | 2010-10-28 | Panasonic Corp | Refrigerator |
| JP2011112242A (en) * | 2009-11-25 | 2011-06-09 | Panasonic Corp | Air conditioner |
| JP2012042158A (en) * | 2010-08-20 | 2012-03-01 | Arai Seisakusho Co Ltd | Food storage |
| JP2013019656A (en) * | 2011-07-14 | 2013-01-31 | Toyota Industries Corp | Combined heat exchanger |
| US20140007610A1 (en) * | 2012-07-06 | 2014-01-09 | Samsung Electronics Co., Ltd. | Refrigerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62171863U (en) * | 1986-03-17 | 1987-10-31 | ||
| JP2000146330A (en) * | 1998-11-04 | 2000-05-26 | Mitsubishi Heavy Ind Ltd | Air conditioner, plate fin tube type heat exchanger, drying cold storage chamber, refrigerant circuit and cooling device |
| JP2001201194A (en) * | 2000-01-18 | 2001-07-27 | Matsushita Refrig Co Ltd | Cold storage system with deep freezer |
| JP2007303777A (en) * | 2006-05-15 | 2007-11-22 | Hitachi Appliances Inc | Refrigerator |
| JP2010243055A (en) * | 2009-04-06 | 2010-10-28 | Panasonic Corp | Refrigerator |
| JP2011112242A (en) * | 2009-11-25 | 2011-06-09 | Panasonic Corp | Air conditioner |
| JP2012042158A (en) * | 2010-08-20 | 2012-03-01 | Arai Seisakusho Co Ltd | Food storage |
| JP2013019656A (en) * | 2011-07-14 | 2013-01-31 | Toyota Industries Corp | Combined heat exchanger |
| US20140007610A1 (en) * | 2012-07-06 | 2014-01-09 | Samsung Electronics Co., Ltd. | Refrigerator |
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