JP2008052751A - Automatic vending machine - Google Patents
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本発明は、缶飲料などの商品を加温あるいは加温と同時に冷却して販売する自動販売機において、圧縮機で圧縮された冷媒が凝縮する際に生じる潜熱を利用して冷却および加温を行う自動販売機に関するものである。 The present invention relates to a vending machine that sells products such as can drinks that are heated or cooled at the same time as they are heated, and uses the latent heat generated when the refrigerant compressed by the compressor condenses to cool and heat the products. It relates to vending machines.
近年、自動販売機に対する消費電力量削減の要求が高まってきており、消費電力量削減手段として、冷却によって生じる廃熱を利用したものが提案されている（例えば、特許文献１参照）。 In recent years, demands for reducing power consumption for vending machines have increased, and as a means for reducing power consumption, one utilizing waste heat generated by cooling has been proposed (for example, see Patent Document 1).
以下、図面を参照しながら従来の自動販売機を説明する。 Hereinafter, a conventional vending machine will be described with reference to the drawings.
図４は従来の自動販売機の冷媒回路図である。 FIG. 4 is a refrigerant circuit diagram of a conventional vending machine.
図４に示すように、従来の自動販売機は、ホット／コールド切換室１、コールド専用室２、第二のコールド専用室３からなる貯蔵室を備え、ホット／コールド切換室１内に設置された室内熱交換器４、コールド専用室２内に設置された蒸発器５、第二のコールド専用室２内に設置された第二の蒸発器６、貯蔵室の外に設置された室外熱交換器７、圧縮機８で構成された冷却加温システムを有する。 As shown in FIG. 4, the conventional vending machine includes a storage room composed of a hot / cold switching room 1, a cold dedicated room 2, and a second cold dedicated room 3, and is installed in the hot / cold switching room 1. Indoor heat exchanger 4, evaporator 5 installed in the cold-dedicated room 2, second evaporator 6 installed in the second cold-dedicated room 2, outdoor heat exchange installed outside the storage room And a cooling and heating system including a compressor 7 and a compressor 8.
また、膨張弁Ａ９、膨張弁Ｂ１０、膨張弁Ｃ１１はそれぞれ通過する冷媒の圧力を低下するとともに閉塞機能を有したものであり、開閉弁Ａ１２、開閉弁Ｂ１３、開閉弁Ｃ１４、開閉弁Ｄ１５はそれぞれ冷媒の流れの有無を制御するものである。 The expansion valve A9, the expansion valve B10, and the expansion valve C11 reduce the pressure of the refrigerant passing therethrough and have a blocking function. The on-off valve A12, the on-off valve B13, the on-off valve C14, and the on-off valve D15 are respectively It controls the presence or absence of refrigerant flow.
また、コンプファン１６は冷却加温システムに連動して駆動し、室外熱交換器７と圧縮機８を冷却するものである。 The comp fan 16 is driven in conjunction with the cooling and heating system to cool the outdoor heat exchanger 7 and the compressor 8.
以上のように構成された従来の自動販売機について、以下その動作を説明する。 The operation of the conventional vending machine configured as described above will be described below.
ホット／コールド切換室１を冷却する場合、開閉弁Ａ１２と開閉弁Ｄ１５を開とし、開閉弁Ｂ１３と開閉弁Ｃ１４を閉として、圧縮機８および冷却ファン１５を駆動する。圧縮機８から吐出された冷媒は、室外熱交換器７で凝縮された後、それぞれ膨張弁Ａ９、膨張弁Ｂ１０、膨張弁Ｃ１１で減圧されて、室内熱交換器４、蒸発器５、第二の蒸発器６へ供給される。そして、室内熱交換器４、蒸発器５、第二の蒸発器６で蒸発した冷媒が圧縮機８へ還流する。 When the hot / cold switching chamber 1 is cooled, the on-off valve A12 and the on-off valve D15 are opened, the on-off valve B13 and the on-off valve C14 are closed, and the compressor 8 and the cooling fan 15 are driven. The refrigerant discharged from the compressor 8 is condensed by the outdoor heat exchanger 7 and then decompressed by the expansion valve A9, the expansion valve B10, and the expansion valve C11, respectively, and the indoor heat exchanger 4, the evaporator 5, and the second To the evaporator 6. Then, the refrigerant evaporated in the indoor heat exchanger 4, the evaporator 5, and the second evaporator 6 is returned to the compressor 8.
このとき、ホット／コールド切換室１、コールド専用室２、第二のコールド専用室３の内所定の温度に達した貯蔵室は、当該する膨張弁Ａ９、膨張弁Ｂ１０、膨張弁Ｃ１１を閉塞して冷媒の供給を停止する。さらに、すべての貯蔵室が所定の温度に達すると圧縮機８の運転を停止する。 At this time, the storage chamber that has reached a predetermined temperature among the hot / cold switching chamber 1, the cold dedicated chamber 2, and the second cold dedicated chamber 3 closes the expansion valve A9, the expansion valve B10, and the expansion valve C11. Stop supplying the refrigerant. Further, when all the storage rooms reach a predetermined temperature, the operation of the compressor 8 is stopped.
次に、ホット／コールド切換室１を加温する場合、開閉弁Ａ１２と開閉弁Ｄ１５および膨張弁Ａ９を閉とし、開閉弁Ｂ１３と開閉弁Ｃ１４を開として、圧縮機８および冷却ファン１５を駆動する。圧縮機８から吐出された冷媒は、室内熱交換器４で一部が凝縮し、再度室外熱交換器７で凝縮された後、それぞれ膨張弁Ｂ１０、膨張弁Ｃ１１で減圧されて、蒸発器５、第二の蒸発器６へ供給される。 Next, when the hot / cold switching chamber 1 is heated, the on-off valve A12, the on-off valve D15, and the expansion valve A9 are closed, the on-off valve B13 and the on-off valve C14 are opened, and the compressor 8 and the cooling fan 15 are driven. To do. The refrigerant discharged from the compressor 8 is partially condensed in the indoor heat exchanger 4 and again condensed in the outdoor heat exchanger 7, and then decompressed by the expansion valve B 10 and the expansion valve C 11, respectively. , And supplied to the second evaporator 6.
そして、蒸発器５、第二の蒸発器６で蒸発した冷媒が圧縮機８へ還流する。また、コールド専用室２、第二のコールド専用室３の内、所定の温度に達した貯蔵室は、当該する膨張弁Ｂ１０、膨張弁Ｃ１１を閉塞して冷媒の供給を停止する。さらに、すべての貯蔵室が所定の温度に達すると圧縮機８の運転を停止する。 Then, the refrigerant evaporated in the evaporator 5 and the second evaporator 6 is returned to the compressor 8. Further, the storage chamber that has reached a predetermined temperature in the cold dedicated chamber 2 and the second cold dedicated chamber 3 closes the expansion valve B10 and the expansion valve C11 to stop the supply of the refrigerant. Further, when all the storage rooms reach a predetermined temperature, the operation of the compressor 8 is stopped.
このように、コールド専用室２および第二のコールド専用室３を冷却する際に生じる冷媒の凝縮廃熱を用いて、ホット／コールド切換室１を効率よく加温することができるので、電気ヒータなどの別の加熱手段を用いてホット／コールド切換室１を加温する場合に比べて、消費電力量を削減することができる。
しかしながら、上記従来の構成では、ホット／コールド切換室を加温すると同時にコールド専用室および第二のコールド専用室を冷却するために、凝縮温度６０℃以上でかつ蒸発温度−１０℃以下を同時に実現する必要があり、このような高圧縮比条件に耐える中低温用圧縮機を新たに開発しなければならないという課題があった。 However, in the above conventional configuration, in order to heat the hot / cold switching chamber and simultaneously cool the cold dedicated chamber and the second cold dedicated chamber, a condensing temperature of 60 ° C. or higher and an evaporation temperature of −10 ° C. or lower are realized at the same time. Therefore, there has been a problem that a medium / low temperature compressor that can withstand such a high compression ratio must be newly developed.
一般に、冷凍空調用圧縮機は蒸発温度が−３０〜−２０℃と比較的低い冷凍向けの低温用圧縮機と、蒸発温度が−１０〜＋１０℃と比較的高い空調向けの高温用圧縮機、およびこれらの中間の蒸発温度−２０〜−１０℃向けの中温用圧縮機に大別される。コールド飲料の温度が５℃、ホット飲料の温度が５５℃の自動販売機においては、コールド飲料を冷却するために中温用圧縮機あるいは低温用圧縮機が用いられる。 In general, a compressor for refrigeration and air conditioning is a low temperature compressor for refrigeration having a relatively low evaporation temperature of −30 to −20 ° C., and a high temperature compressor for air conditioning having a relatively high evaporation temperature of −10 to + 10 ° C., And these are roughly classified into medium temperature compressors for an intermediate evaporation temperature of -20 to -10 ° C. In a vending machine having a cold beverage temperature of 5 ° C. and a hot beverage temperature of 55 ° C., an intermediate temperature compressor or a low temperature compressor is used to cool the cold beverage.
また、これらの圧縮機を用いるシステムは、常温大気と熱交換することを前提に設計されているため、通常、圧縮機の使用範囲は凝縮温度６０℃以下に制限されている。従って、ホット飲料周囲の高温雰囲気を加温するためにはこの制限を越えた凝縮温度６０〜８０℃に耐える圧縮機の開発が不可欠である。結果として、コールド飲料とホット飲料を同一システムで実現するためには、蒸発温度−３０〜−１０℃でかつ凝縮温度６０〜８０℃の範囲で使用可能な圧縮機を新たに開発する必要がある。 Moreover, since the system using these compressors is designed on the assumption that heat is exchanged with room temperature air, the use range of the compressor is usually limited to a condensation temperature of 60 ° C. or lower. Therefore, in order to heat the high temperature atmosphere around the hot beverage, it is indispensable to develop a compressor that can withstand a condensation temperature of 60 to 80 ° C. exceeding this limit. As a result, in order to realize a cold beverage and a hot beverage in the same system, it is necessary to newly develop a compressor that can be used at an evaporation temperature of −30 to −10 ° C. and a condensation temperature of 60 to 80 ° C. .
また、上記従来の構成では、凝縮圧力と蒸発圧力の比である圧縮比が大きくなるため、理論冷凍能力および圧縮機の体積効率が低下して、システムの冷却能力が著しく低下する。そのために、高能力の圧縮機および冷媒の使用が不可欠であり、この結果として理論効率が低く、かつ高圧圧力が高いＲ４０７ＣやＲ２９０などの低沸点冷媒を使わなければならないという課題があった。 In the conventional configuration, the compression ratio, which is the ratio between the condensation pressure and the evaporation pressure, increases, so that the theoretical refrigeration capacity and the volumetric efficiency of the compressor are reduced, and the cooling capacity of the system is significantly reduced. Therefore, the use of a high-capacity compressor and refrigerant is indispensable, and as a result, there is a problem that low-boiling refrigerants such as R407C and R290 having low theoretical efficiency and high high pressure must be used.
本発明は、従来の課題を解決するもので、圧縮機の動作条件に着目して効率が高く容易に実現できる冷却加温システムを提案し、加温時の消費電力量を削減できる自動販売機を提供することを目的とする。 The present invention solves the conventional problems, proposes a cooling and heating system that can be realized easily with high efficiency by paying attention to the operating conditions of the compressor, and a vending machine that can reduce power consumption during heating The purpose is to provide.
上記従来の課題を解決するために、本発明の自動販売機は、ホット／コールド切替室の冷却運転と加温運転を切替え可能な冷却加温システムと、前記冷却加温システムに備えられた冷温用圧縮機とを備えた自動販売機であって、前記冷温用圧縮機は複数の回転数で運転されるインバータ圧縮機であり、加温運転時における安定時の最高運転回転数は冷却運転時における安定時の最高運転回転数よりも低運転回転数としたことを特徴とするものである。 In order to solve the above conventional problems, a vending machine according to the present invention includes a cooling / heating system capable of switching between a cooling operation and a heating operation of a hot / cold switching chamber, and a cooling / heating temperature provided in the cooling / heating system. A compressor for cooling and cooling, wherein the compressor for cooling and heating is an inverter compressor that is operated at a plurality of rotation speeds, and the maximum operating rotation speed at the time of heating operation is stable during cooling operation. The operating speed is lower than the maximum operating speed at the time of stability.
これによって、ホット／コールド切換室を加温する場合、圧縮機は低回転で制御されるので、高い回転数で運転した場合に能力過剰となり室内凝縮器の温度が圧縮機の限界を越えて上昇し、耐久性の低下を招くとともに、能力過剰となり圧縮機を断続運転する必要が生じ、停止状態から室内凝縮器の温度が所定温度に達するまでの無駄な運転が生じて、全体として効率の低下を招くことを防止することができる。 As a result, when the hot / cold switching chamber is heated, the compressor is controlled at a low speed, so that the capacity becomes excessive when operating at a high speed, and the temperature of the indoor condenser rises beyond the limit of the compressor. As a result, the durability is reduced, the capacity becomes excessive, and the compressor needs to be intermittently operated. As a result, useless operation from the stop state until the temperature of the indoor condenser reaches a predetermined temperature occurs, resulting in a decrease in efficiency as a whole. Can be prevented.
本発明の自動販売機は、室内加温時、圧縮機を低回転で制御されるので、圧縮機を高回転で運転した場合に断続運転となって無駄な運転が生じ、全体として効率の低下を招くことを防止し、圧縮機の高効率化を図り、自動販売機の消費電力量を大幅に削減することができる。 In the vending machine of the present invention, the compressor is controlled at a low speed during indoor warming, so when the compressor is operated at a high speed, intermittent operation occurs and wasteful operation occurs, resulting in a decrease in efficiency as a whole. Can be prevented, the efficiency of the compressor can be increased, and the power consumption of the vending machine can be greatly reduced.
本発明の請求項１に記載の発明は、ホット／コールド切替室の冷却運転と加温運転を切替え可能な冷却加温システムと、前記冷却加温システムに備えられた冷温用圧縮機とを備えた自動販売機であって、前記冷温用圧縮機は複数の回転数で運転されるインバータ圧縮機であり、加温運転時における安定時の最高運転回転数は冷却運転時における安定時の最高運転回転数よりも低運転回転数としたことを特徴とするので、高回転で運転した場合に断続運転する必要が生じ、圧縮機の停止状態から室内凝縮器の温度が所定温度に達するまでの無駄な運転が生じて、全体として効率の低下を招くことを防止し、圧縮機の高効率化を図り、自動販売機の消費電力量を大幅に削減することができる。 The invention according to claim 1 of the present invention includes a cooling / heating system capable of switching between a cooling operation and a heating operation of the hot / cold switching chamber, and a cooling / heating compressor provided in the cooling / heating system. The cooling compressor is an inverter compressor that is operated at a plurality of rotational speeds, and the maximum operating rotational speed when the heating operation is stable is the maximum operating speed when the cooling operation is stable. Since the engine speed is lower than the engine speed, it is necessary to perform intermittent operation when operating at a high speed, which is a waste of time until the temperature of the indoor condenser reaches the specified temperature after the compressor is stopped. Therefore, it is possible to prevent a reduction in efficiency as a whole and to increase the efficiency of the compressor and to greatly reduce the power consumption of the vending machine.
本発明の請求項２に記載の発明は、請求項１に記載の発明に、ホット／コールド切換室の加温時のプルアップ時間に冷温用圧縮機と補助ヒータとを運転して加温し、プルアップ時間の短縮を行うことができる。 The invention according to claim 2 of the present invention is the same as that of claim 1 except that the cooling / heating compressor and the auxiliary heater are operated and heated during the pull-up time when the hot / cold switching chamber is heated. The pull-up time can be shortened.
本発明の請求項３に記載の発明は、請求項１または２に記載の発明にさらに、商品を収納し冷却するコールド専用室と、前記コールド専用室の冷却運転を行う冷却システムの冷却用圧縮機とを有し、冷却加温システムとは別に独立した前記冷却システムを備えたことで、ホット／コールド切換室を加温する場合に、コールド専用室の冷却とは関係なく、冷却加温システムの室外熱交換器の蒸発温度を−１０〜１０℃の高温条件に維持して圧縮比を低減することができる。 According to a third aspect of the present invention, in addition to the first or second aspect of the present invention, a cold exclusive chamber for storing and cooling goods, and a cooling compression for a cooling system for performing a cooling operation of the cold exclusive chamber When the hot / cold switching chamber is heated, the cooling and heating system is independent of the cooling of the cold dedicated chamber. The compression temperature can be reduced by maintaining the evaporation temperature of the outdoor heat exchanger at a high temperature condition of −10 to 10 ° C.
本発明の請求項４に記載の発明は、請求項１から３のいずれか一項に記載の発明において、冷却加温システムを循環する冷媒をＲ１３４ａやＲ６００ａなどの高沸点冷媒としたことを特徴とする自動販売機であるので、加温時の室内熱交換器の高温条件に適した高沸点冷媒を使用することで高効率が実現できる。 The invention according to claim 4 of the present invention is characterized in that, in the invention according to any one of claims 1 to 3, the refrigerant circulating through the cooling and heating system is a high boiling point refrigerant such as R134a or R600a. Therefore, high efficiency can be realized by using a high boiling point refrigerant suitable for the high temperature condition of the indoor heat exchanger during heating.
一例として、冷凍機器に使用されている各種冷媒について、蒸発温度−１５℃／凝縮温度７０℃の条件での低圧圧力、高圧圧力、圧縮比、吐出ガス温度、および体積能力と理論効率の相対値を（表１）に、蒸発温度５℃／凝縮温度７０℃の条件での低圧圧力、高圧圧力、圧縮比、吐出ガス温度、および体積能力と理論効率の相対値を（表２）に示す。ここで、（表１）および（表２）の値は、過冷却０℃、吸入ガス温度３２℃、断熱圧縮条件での計算値である。なお、（表１）および（表２）におけるＲ４０７Ｃは液相線と気相線の平均温度が所定温度になる低圧圧力および高圧圧力を選定している。 As an example, for various refrigerants used in refrigeration equipment, low pressure, high pressure, compression ratio, discharge gas temperature, and relative values of volume capacity and theoretical efficiency under the conditions of evaporation temperature −15 ° C./condensation temperature 70 ° C. (Table 1) shows the relative values of low pressure, high pressure, compression ratio, discharge gas temperature, volume capacity and theoretical efficiency under the conditions of evaporation temperature 5 ° C./condensation temperature 70 ° C. Here, the values in (Table 1) and (Table 2) are calculated values under supercooling 0 ° C., intake gas temperature 32 ° C., and adiabatic compression conditions. Incidentally, R407C in (Table 1) and (Table 2) selects a low pressure and a high pressure at which the average temperature of the liquid phase line and the gas phase line becomes a predetermined temperature.
（表１）に示したように、蒸発温度−１５℃／凝縮温度７０℃の条件では、高沸点冷媒であるＲ１３４ａやＲ６００ａを用いると圧縮比が１２を越えることから、過圧縮が発生する実際の動作条件において吐出ガス温度が異常に上昇して圧縮機の耐久性が低下することが懸念されるとともに、低沸点冷媒であるＲ４０７ＣやＲ２９０を用いると高圧圧力が２．５ＭＰａを越えることから、軸受け部の耐荷重性が不足して異常摩耗が発生し圧縮機の耐久性が低下することが懸念される。 As shown in (Table 1), under the conditions of evaporation temperature −15 ° C./condensation temperature 70 ° C., when R134a or R600a, which is a high boiling point refrigerant, is used, the compression ratio exceeds 12, so that over compression occurs. There is a concern that the discharge gas temperature will rise abnormally under the operating conditions of the above, and the durability of the compressor will decrease, and if the low boiling point refrigerants R407C and R290 are used, the high pressure exceeds 2.5 MPa, There is a concern that the load resistance of the bearing portion is insufficient, abnormal wear occurs, and the durability of the compressor decreases.
一方、（表２）に示したように、蒸発温度５℃／凝縮温度７０℃の条件では、高沸点冷媒であるＲ１３４ａやＲ６００ａを用いると圧縮比が９以下となり通常の使用可能範囲となる。さらに、Ｒ６００ａはＲ１３４ａに比べて体積能力が小さくかつ高効率であるので、自販機の断熱材で囲われた貯蔵室を加温する加温システムのように小能力かつ高効率を要求される用途に適している。なお、この凝縮温度条件では、低沸点冷媒であるＲ４０７ＣやＲ２９０を用いると高圧圧力が増大して圧縮機の耐久性に問題が生じることに変わりはない。 On the other hand, as shown in (Table 2), under the conditions of evaporation temperature 5 ° C./condensation temperature 70 ° C., when R134a or R600a, which is a high boiling point refrigerant, is used, the compression ratio becomes 9 or less, which is a normal usable range. Furthermore, since R600a has a smaller volume capacity and higher efficiency than R134a, it is suitable for applications that require small capacity and high efficiency, such as a heating system that heats a storage room surrounded by heat insulating material of a vending machine. Is suitable. Under these condensing temperature conditions, the use of R407C or R290, which are low boiling point refrigerants, will cause a problem in the durability of the compressor due to an increase in the high pressure.
また、シェル内が蒸発圧力で維持されるレシプロ型圧縮機を用いることで、断続運転時に凝縮圧力が庫内温度相当の圧力まで立ち上がる特性に優れ、圧縮機の断続に伴う加温ロスを削減して高効率化が図れる。 In addition, by using a reciprocating compressor in which the inside of the shell is maintained at the evaporation pressure, the condensation pressure rises to a pressure equivalent to the internal temperature during intermittent operation, reducing the heating loss associated with intermittent compressor operation. Increase efficiency.
以下、本発明による自動販売機の実施の形態について図面を参照しながら説明する。なお、従来と同一構成については、同一符号を付して詳細な説明を省略する。 Embodiments of a vending machine according to the present invention will be described below with reference to the drawings. In addition, about the same structure as the past, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.
（実施の形態１）
図１は本発明の実施の形態１の自動販売機の冷媒回路図である。
(Embodiment 1)
FIG. 1 is a refrigerant circuit diagram of a vending machine according to Embodiment 1 of the present invention.
図１に示すように、本発明の自動販売機は、ホット／コールド切換室１、コールド専用室２、第二のコールド専用室３からなる貯蔵室を備え、Ｒ６００ａを冷媒とし、高温用レシプロ型圧縮機２０、ホット／コールド切換室１内に設置された室内蒸発器２１および室内凝縮器２２、貯蔵室の外に設置された室外蒸発器２３および室外凝縮器２４、冷却時と加温時に冷媒流路を切換える三方切換弁２５、冷却用膨張弁２６、加温用膨張弁２７からなり、ホット／コールド切換室１の冷却と加温を専用に行う冷却加温システムを有する。 As shown in FIG. 1, the vending machine according to the present invention includes a storage chamber composed of a hot / cold switching chamber 1, a cold dedicated chamber 2, and a second cold dedicated chamber 3. R600a is used as a refrigerant, and a reciprocating type for high temperatures. Compressor 20, indoor evaporator 21 and indoor condenser 22 installed in hot / cold switching chamber 1, outdoor evaporator 23 and outdoor condenser 24 installed outside the storage room, refrigerant during cooling and heating A three-way switching valve 25 that switches the flow path, a cooling expansion valve 26, and a heating expansion valve 27 are provided, and a cooling and heating system that exclusively cools and heats the hot / cold switching chamber 1 is provided.
また、室内凝縮器２２は室内蒸発器２１や蒸発器５、第二の蒸発器６と同様にフィンチューブ熱交換器の形態であるが、着霜を考慮せず高い凝縮能力を優先して、フィン間隔やチューブ間隔を比較的狭めるとともに冷媒と空気の流れが対向流となるようにチューブの接続が設計されている。この結果、凝縮温度と吸込み空気温度との差が１０℃において、２００〜３００Ｗの加温能力を有している。 Moreover, the indoor condenser 22 is in the form of a fin tube heat exchanger like the indoor evaporator 21, the evaporator 5 and the second evaporator 6, but giving priority to a high condensation capacity without considering frost formation, The tube connection is designed so that the fin interval and the tube interval are relatively narrow and the refrigerant and air flows in opposite directions. As a result, when the difference between the condensation temperature and the intake air temperature is 10 ° C., it has a heating capacity of 200 to 300 W.
一方、室外蒸発器２３は低外気温度での着霜を考慮して、室内蒸発器２１や蒸発器５、第二の蒸発器６と同様に設計されている。 On the other hand, the outdoor evaporator 23 is designed similarly to the indoor evaporator 21, the evaporator 5, and the second evaporator 6 in consideration of frost formation at a low outside air temperature.
また、冷却用膨張弁２６および加温用膨張弁２７は通過する冷媒の圧力を低下して蒸発圧力を調整するものである。特に、凝縮温度がまだ上昇していない起動直後に、加温用膨張弁２７の開度を大きくして循環量を増大することで、凝縮温度の立ち上がり特性を改善することができる。 The cooling expansion valve 26 and the heating expansion valve 27 are for adjusting the evaporation pressure by lowering the pressure of the refrigerant passing therethrough. In particular, immediately after the start-up when the condensing temperature has not risen, the rise of the condensing temperature can be improved by increasing the opening amount of the heating expansion valve 27 and increasing the circulation rate.
また、コンプファン２８はホット／コールド切換室１の冷却時に駆動して運転中の高温用レシプロ型圧縮機２０を常に冷却するとともに、ホット／コールド切換室１の加温時に高温用レシプロ型圧縮機２０が８０℃以上の異常に高い温度になった時に駆動して、７０℃以下で安定するまで高温用レシプロ型圧縮機２０を冷却するものである。 In addition, the compressor fan 28 is driven when the hot / cold switching chamber 1 is cooled to always cool the high-temperature reciprocating compressor 20 during operation, and the hot / cold switching chamber 1 is heated when the hot / cold switching chamber 1 is heated. It is driven when 20 reaches an abnormally high temperature of 80 ° C. or higher, and the reciprocating compressor 20 for high temperature is cooled until stabilized at 70 ° C. or lower.
ここで、高温用レシプロ型圧縮機２０は、Ｒ１３４ａを冷媒とする家庭用冷蔵庫に使用されている低温用レシプロ型圧縮機に、冷媒Ｒ６００ａと鉱油系冷凍機油をドロップインしたものである。この低温用レシプロ型圧縮機は、ＤＣインバータで駆動され、標準条件である凝縮温度５４．４℃、蒸発温度−２３．３℃における冷凍能力に換算して１００〜２５０Ｗの範囲で能力可変することができる。同様に、冷媒Ｒ６００ａと鉱油系冷凍機油をドロップインした高温用レシプロ型圧縮機２０は、凝縮温度５４．４℃、蒸発温度−１２．２℃の冷却条件において７０〜１８０Ｗの冷凍能力を有するとともに、凝縮温度７０℃、蒸発温度５℃の加温条件において１６０〜４００Ｗの加温能力を有する。 Here, the high-temperature reciprocating compressor 20 is obtained by dropping refrigerant R600a and mineral oil-based refrigerating machine oil into a low-temperature reciprocating compressor used in a household refrigerator using R134a as a refrigerant. This low-temperature reciprocating compressor is driven by a DC inverter, and its capacity can be varied in the range of 100 to 250 W in terms of refrigeration capacity at a condensing temperature of 54.4 ° C. and an evaporation temperature of −23.3 ° C., which are standard conditions. Can do. Similarly, the high-temperature reciprocating compressor 20 in which the refrigerant R600a and the mineral oil refrigerating machine oil are dropped in has a refrigerating capacity of 70 to 180 W under cooling conditions of a condensation temperature of 54.4 ° C. and an evaporation temperature of 12.2 ° C. In addition, it has a heating capacity of 160 to 400 W under heating conditions of a condensation temperature of 70 ° C. and an evaporation temperature of 5 ° C.
また、低温用一定速圧縮機２９は室外熱交換器７、蒸発器５および第二の蒸発器６、膨張弁Ｂ１０および膨張弁Ｃ１１とともに冷却サイクルを構成し、コールド専用室２、第二のコールド専用室３を冷却するものである。低温用一定速圧縮機２９はＲ６００ａを冷媒とする家庭用冷蔵庫に用いられる圧縮機であり、凝縮温度５４．４℃、蒸発温度−１２．２℃の冷却条件において約２５０Ｗの冷凍能力を有する。 The low-temperature constant-speed compressor 29 constitutes a cooling cycle together with the outdoor heat exchanger 7, the evaporator 5 and the second evaporator 6, the expansion valve B10 and the expansion valve C11. The dedicated chamber 3 is cooled. The low-temperature constant speed compressor 29 is a compressor used in a household refrigerator using R600a as a refrigerant, and has a refrigerating capacity of about 250 W under cooling conditions of a condensation temperature of 54.4 ° C. and an evaporation temperature of 12.2 ° C.
以上のように構成された実施の形態１の自動販売機について、以下その動作を説明する。 The operation of the vending machine of the first embodiment configured as described above will be described below.
ホット／コールド切換室１を冷却する場合、三方切換弁２５を冷却側に切換えて高温用レシプロ型圧縮機２０を駆動する。高温用レシプロ型圧縮機２０から吐出された冷媒は、三方切換弁２５を経由して室外凝縮器２４で凝縮された後、冷却用膨張弁２６で減圧されて、室内蒸発器２１へ供給される。そして、室内蒸発器２１で蒸発した冷媒が高温用レシプロ型圧縮機２０へ還流する。 When the hot / cold switching chamber 1 is cooled, the three-way switching valve 25 is switched to the cooling side to drive the high temperature reciprocating compressor 20. The refrigerant discharged from the high-temperature reciprocating compressor 20 is condensed by the outdoor condenser 24 via the three-way switching valve 25, then decompressed by the cooling expansion valve 26, and supplied to the indoor evaporator 21. . Then, the refrigerant evaporated in the indoor evaporator 21 returns to the high-temperature reciprocating compressor 20.
このとき、ホット／コールド切換室１が所定の温度に近づくと高温用レシプロ型圧縮機２０を減速して能力を低下することにより、蒸発温度を上げて冷却効率を向上する。例えば外気温度１５℃ではホット／コールド切換室１の安定時の熱負荷は１００〜２００Ｗ程度であるので、高温用レシプロ型圧縮機２０は蒸発温度−２０〜−１５℃、凝縮温度３０〜４０℃の運転条件で５８〜７２ｒｐｓの高回転で略連続運転するように制御される。そして、ホット／コールド切換室１が所定の温度に達すると高温用レシプロ型圧縮機２０の運転を停止する。 At this time, when the hot / cold switching chamber 1 approaches a predetermined temperature, the high-temperature reciprocating compressor 20 is decelerated to reduce the capacity, thereby raising the evaporation temperature and improving the cooling efficiency. For example, since the heat load when the hot / cold switching chamber 1 is stable is about 100 to 200 W at an outside air temperature of 15 ° C., the reciprocating compressor 20 for high temperature has an evaporation temperature of −20 to −15 ° C. and a condensation temperature of 30 to 40 ° C. It is controlled to operate substantially continuously at a high rotation speed of 58 to 72 rps under the above operating conditions. When the hot / cold switching chamber 1 reaches a predetermined temperature, the operation of the high-temperature reciprocating compressor 20 is stopped.
また、例えば外気温度１５℃でプルダウンする場合は、ホット／コールド切換室１の温度が高いために室内蒸発器２１の蒸発温度が上昇して冷却能力が増大する、すなわち能力の自動調整機能が働くことから、特に冷却用膨張弁２６の開度や高温用レシプロ型圧縮機２０の能力を細かく制御する必要はなく、安定時に合わせて固定してもよい。 For example, when pulling down at an outside air temperature of 15 ° C., the temperature of the hot / cold switching chamber 1 is high, so that the evaporation temperature of the indoor evaporator 21 increases and the cooling capacity increases, that is, the automatic capacity adjustment function works. Therefore, it is not particularly necessary to finely control the opening degree of the cooling expansion valve 26 and the capability of the high-temperature reciprocating compressor 20, and they may be fixed at a stable time.
一方、ホット／コールド切換室１を加温する場合、三方切換弁２５を加温側に切換えて高温用レシプロ型圧縮機２０を駆動する。高温用レシプロ型圧縮機２０から吐出された冷媒は、三方切換弁２５を経由して室内凝縮器２２で凝縮された後、加温用膨張弁２７で減圧されて、室外蒸発器２３へ供給される。そして、室外蒸発器２３で蒸発した冷媒が高温用レシプロ型圧縮機２０へ還流する。 On the other hand, when the hot / cold switching chamber 1 is heated, the high-temperature reciprocating compressor 20 is driven by switching the three-way switching valve 25 to the heating side. The refrigerant discharged from the high-temperature reciprocating compressor 20 is condensed by the indoor condenser 22 via the three-way switching valve 25, then decompressed by the heating expansion valve 27, and supplied to the outdoor evaporator 23. The Then, the refrigerant evaporated in the outdoor evaporator 23 returns to the high-temperature reciprocating compressor 20.
このとき、例えば外気温度１５℃ではホット／コールド切換室１の安定時の熱負荷は１００〜２００Ｗ程度であるので、高温用レシプロ型圧縮機２０は蒸発温度５〜１０℃、凝縮温度５５〜６５℃の運転条件で２７〜３５ｒｐｓの低回転で連続運転するように制御される。これは、より高い回転数で運転した場合、能力過剰となり室内凝縮器２２の凝縮温度が高温用レシプロ圧縮機２０の限界を越えて上昇し、耐久性の低下を招くとともに、能力過剰となり高温用レシプロ圧縮機２０を断続運転する必要が生じ、停止状態から室内凝縮器２２の温度が所定温度に達するまでの無駄な運転が生じて全体として効率の低下を招くためである。 At this time, for example, when the outside air temperature is 15 ° C., the stable heat load of the hot / cold switching chamber 1 is about 100 to 200 W, so the high-temperature reciprocating compressor 20 has an evaporation temperature of 5 to 10 ° C. and a condensation temperature of 55 to 65. It is controlled so as to continuously operate at a low rotation of 27 to 35 rps under the operating condition of ° C. This is because when the engine is operated at a higher rotational speed, the capacity becomes excessive and the condensation temperature of the indoor condenser 22 rises beyond the limit of the high-temperature reciprocating compressor 20, leading to a decrease in durability and excessive capacity. This is because the reciprocating compressor 20 needs to be intermittently operated, and a wasteful operation from the stop state until the temperature of the indoor condenser 22 reaches a predetermined temperature occurs, resulting in a decrease in efficiency as a whole.
また、例えば外気温度１５℃でプルアップする場合は、ホット／コールド切換室１を通常４００Ｗ程度で加温する必要がある。この場合、高温用レシプロ圧縮機２０は蒸発温度＋０〜＋５℃、凝縮温度７０〜７５℃の運転条件で７２ｒｐｓの高回転で連続運転するように制御される。ここで、重要な点は、プルダウンする場合に見られる能力の自動調整機構がプルアップする場合には働かず、ホット／コールド切換室１の温度が低い時には凝縮温度が低くなり、逆に加温能力が低下する傾向があるために、加温能力を高める制御が不可欠となる点である。例えば、加温用膨張弁２７の開度を開けて高温用レシプロ圧縮機２０を高回転で連続運転するとともに、高温用レシプロ圧縮機２０の表面での無駄な放熱を抑制するためにコンプファン２８を停止することが望ましい。 For example, when pulling up at an outside air temperature of 15 ° C., it is necessary to heat the hot / cold switching chamber 1 at about 400 W. In this case, the high-temperature reciprocating compressor 20 is controlled so as to continuously operate at a high rotation speed of 72 rps under operating conditions of an evaporation temperature +0 to + 5 ° C. and a condensation temperature 70 to 75 ° C. Here, the important point is that the automatic adjustment mechanism of the capacity seen when pulling down does not work when pulling up, and when the temperature of the hot / cold switching chamber 1 is low, the condensing temperature becomes low, and conversely the heating Since the ability tends to decrease, control for increasing the heating ability is indispensable. For example, the opening of the heating expansion valve 27 is opened to continuously operate the high-temperature reciprocating compressor 20 at a high speed, and the comp fan 28 is used to suppress wasteful heat radiation on the surface of the high-temperature reciprocating compressor 20. It is desirable to stop.
従って、本実施例の構成において効率よくホット／コールド切換室１の冷却と加温を実現するには、プルダウン中は高温用レシプロ圧縮機２０の回転数を比較的高回転で維持すればよいが、プルアップ中にはホット／コールド切換室１内の温度が上昇するに伴って、高温用レシプロ圧縮機２０の回転数を２７〜３５ｒｐｓまで順次低下させて能力調整する必要がある。また、ホット／コールド切換室１内の温度が上昇する過程で、凝縮温度が高温用レシプロ圧縮機２０の限界を越えないように、望ましくは、室内凝縮器２２の凝縮温度を検知する温度センサーを設けるとともに、室内凝縮器２２の凝縮温度が所定値を越えると高温用レシプロ圧縮機２０の回転数を下げる制御を行う方がよい。 Accordingly, in order to efficiently cool and warm the hot / cold switching chamber 1 in the configuration of the present embodiment, the rotational speed of the high-temperature reciprocating compressor 20 may be maintained at a relatively high speed during pull-down. During the pull-up, as the temperature in the hot / cold switching chamber 1 rises, it is necessary to adjust the capacity by sequentially decreasing the rotational speed of the high-temperature reciprocating compressor 20 to 27 to 35 rps. Further, a temperature sensor for detecting the condensation temperature of the indoor condenser 22 is preferably provided so that the condensation temperature does not exceed the limit of the high-temperature reciprocating compressor 20 in the process of increasing the temperature in the hot / cold switching chamber 1. In addition, when the condensation temperature of the indoor condenser 22 exceeds a predetermined value, it is better to perform control to reduce the rotational speed of the high-temperature reciprocating compressor 20.
コールド専用室２、第二のコールド専用室３を冷却する場合、低温用一定速圧縮機２９を駆動する。低温用一定速圧縮機２９から吐出された冷媒は、室外熱交換器７で凝縮された後、膨張弁Ｂ１０および膨張弁Ｃ１１で減圧されて、それぞれ蒸発器５および第二の蒸発器６へ供給される。そして、蒸発器５および第二の蒸発器６で蒸発した冷媒が低温用一定速圧縮機２９へ還流する。 When cooling the cold exclusive chamber 2 and the second cold exclusive chamber 3, the low-temperature constant speed compressor 29 is driven. The refrigerant discharged from the low-temperature constant speed compressor 29 is condensed by the outdoor heat exchanger 7 and then decompressed by the expansion valve B10 and the expansion valve C11 and supplied to the evaporator 5 and the second evaporator 6, respectively. Is done. Then, the refrigerant evaporated in the evaporator 5 and the second evaporator 6 is returned to the low-temperature constant speed compressor 29.
このとき、コールド専用室２、第二のコールド専用室３が所定の温度に達すると、該当する膨張弁Ｂ１０あるいは膨張弁Ｃ１１を閉塞し、コールド専用室２と第二のコールド専用室３がともに所定の温度に達すると、低温用一定速圧縮機２９の運転を停止する。例えば外気温度１５℃ではコールド専用室２、第二のコールド専用室３の安定時の熱負荷は１００〜３００Ｗ程度であるので、低温用一定速圧縮機２９は蒸発温度−２５〜−１５℃、凝縮温度３０〜４０℃の運転条件で断続運転する。 At this time, when the cold dedicated chamber 2 and the second cold dedicated chamber 3 reach a predetermined temperature, the corresponding expansion valve B10 or expansion valve C11 is closed, and both the cold dedicated chamber 2 and the second cold dedicated chamber 3 are When the temperature reaches a predetermined temperature, the operation of the constant temperature compressor 29 for low temperature is stopped. For example, when the outside air temperature is 15 ° C., the stable heat load of the cold dedicated chamber 2 and the second cold dedicated chamber 3 is about 100 to 300 W, so the low temperature constant speed compressor 29 has an evaporation temperature of −25 to −15 ° C. Intermittent operation is performed under operating conditions of a condensation temperature of 30 to 40 ° C.
従って、従来ホット／コールド切換室１およびコールド専用室２、第二のコールド専用室３を同時に冷却するために、低沸点冷媒であるＲ４０７Ｃを冷媒とし、凝縮温度５４．４℃、蒸発温度−１２．２℃の冷却条件において４００〜６００Ｗの冷凍能力を有する圧縮機１台を搭載していたが、本実施例の構成のようにホット／コールド切換室１の冷却を高温用レシプロ型圧縮機２０で行い、コールド専用室２および第二のコールド専用室３の冷却を低温用一定速圧縮機２９で行うことで、それぞれ効率の高い高沸点冷媒であるＲ６００ａを冷媒とし、小能力であるが家庭用冷蔵庫に使用されている安価で圧縮機効率の高い圧縮機を用いることができ、冷却時においてもより効率化が図れる。 Therefore, in order to simultaneously cool the conventional hot / cold switching chamber 1, the cold dedicated chamber 2, and the second cold dedicated chamber 3, the low boiling point refrigerant R407C is used as the refrigerant, the condensation temperature is 54.4 ° C., and the evaporation temperature is −12. Although one compressor having a refrigeration capacity of 400 to 600 W under the cooling condition of 2 ° C. was mounted, the hot / cold switching chamber 1 was cooled with a high temperature reciprocating compressor 20 as in the configuration of this embodiment. The cold dedicated chamber 2 and the second cold dedicated chamber 3 are cooled by the low-temperature constant speed compressor 29, so that R600a, which is a high-efficiency high-boiling-point refrigerant, is used as the refrigerant. Therefore, it is possible to use an inexpensive compressor with high compressor efficiency that is used in a refrigerator, and the efficiency can be improved even during cooling.
コールド専用室２、第二のコールド専用室３をプルダウンする場合は、ホット／コールド切換室１の冷却時と同様に、能力の自動調整機能が働くので、膨張弁Ｂ１０あるいは膨張弁Ｃ１１を細かく調整する必要はない。また、コールド専用室２、第二のコールド専用室３の内片方だけを冷却する状態では、一方の膨張弁が閉塞して循環量が低下するので蒸発温度が−２０℃以下に下がって能力調整される。 When pulling down the cold-dedicated chamber 2 and the second cold-dedicated chamber 3, the automatic capacity adjustment function works in the same way as when the hot / cold switching chamber 1 is cooled. Therefore, the expansion valve B10 or the expansion valve C11 is finely adjusted. do not have to. In addition, in the state where only one of the cold exclusive chamber 2 and the second cold exclusive chamber 3 is cooled, one expansion valve is closed and the circulation amount is lowered, so the evaporation temperature is lowered to -20 ° C. or less to adjust the capacity. Is done.
なお、本実施の形態においては、１５℃における冷却安定時のホット／コールド切換室１の冷却負荷を１００〜２００Ｗ程度、加温安定時のホット／コールド切換室１の加温負荷を１００〜２００Ｗ程度である標準的な自動販売機を想定したが、他の自動販売機においても１５〜２５℃の常温付近では冷却負荷と加温負荷はほぼ同程度であるとともに、加温時に比べて冷却時の蒸発温度が低いことから、加温安定時の過剰な加温能力を抑制するために高温用レシプロ型圧縮機２０の能力を低減する必要がある点に変わりはない。 In the present embodiment, the cooling load of the hot / cold switching chamber 1 when cooling is stable at 15 ° C. is about 100 to 200 W, and the heating load of the hot / cold switching chamber 1 when heating is stable is 100 to 200 W. A standard vending machine is assumed, but in other vending machines, the cooling load and the heating load are approximately the same at around 15 to 25 ° C, and the cooling time is lower than the heating time. Since the evaporation temperature is low, there is no change in that it is necessary to reduce the capacity of the high-temperature reciprocating compressor 20 in order to suppress excessive warming capacity during stable heating.
なお、本実施の形態においては、ホット／コールド切換室１の加温時のプルアップを冷却加温システムの加温能力でのみ実現したが、プルアップの初期のみ補助ヒータを用いてホット／コールド切換室１あるいは室内凝縮器２２を加温して、プルアップ時間の短縮を図ってもよい。 In the present embodiment, the pull-up at the time of heating the hot / cold switching chamber 1 is realized only by the heating capability of the cooling / heating system, but the hot / cold is used by using the auxiliary heater only at the initial stage of the pull-up. The switching chamber 1 or the indoor condenser 22 may be heated to shorten the pull-up time.
なお、本実施の形態においては、ホット／コールド切換室１を加温する場合の室外蒸発器２３の蒸発温度を０〜１０℃の効率の高い範囲で任意に調整したが、特に自動販売機が室内に設置されて結露水が排出できない場合は、結露しない範囲でのみ冷却加温システムを稼動し、雨天などの高湿度条件では補助ヒータのみによる加温に切換えることが望ましい。 In this embodiment, the evaporation temperature of the outdoor evaporator 23 when the hot / cold switching chamber 1 is heated is arbitrarily adjusted within a high efficiency range of 0 to 10 ° C. If it is installed indoors and condensed water cannot be discharged, it is desirable to operate the cooling and heating system only within the range where condensation does not occur, and to switch to heating only with an auxiliary heater under high humidity conditions such as rainy weather.
また、本実施の形態においては、冷却用膨張弁２６、加温用膨張弁２７を用いたが、キャピラリチューブなどの固定絞りを用いてもよい。特に、ホット／コールド切換室１の冷却時は抵抗を微調整する必要がなく、キャピラリチューブを用いて高温用レシプロ型圧縮機２０の吸入配管と熱交換することで冷凍効果を高めることができる。 In this embodiment, the cooling expansion valve 26 and the heating expansion valve 27 are used. However, a fixed throttle such as a capillary tube may be used. In particular, when the hot / cold switching chamber 1 is cooled, it is not necessary to finely adjust the resistance, and the refrigeration effect can be enhanced by exchanging heat with the suction pipe of the high-temperature reciprocating compressor 20 using a capillary tube.
以上のように、本実施の形態においては、コールド専用室および第二のコールド専用室の冷却手段とは別に、ホット／コールド切換室を冷却加温する専用の冷却加温システムを有するとともに、この冷却加温システムとして、Ｒ６００ａを冷媒とする高温用レシプロ型圧縮機と、室内凝縮器と、室内蒸発器と、室外凝縮器と、室外蒸発器と、三方切換弁を備えたことによって、専用に設計された室外蒸発器で室外の大気と熱交換することで、蒸発温度−１０〜１０℃の高温条件に維持して圧縮比を低減することができるとともに、Ｒ６００ａを冷媒とする高温用レシプロ型圧縮機を用いることで、大量に生産されているＲ１３４ａを冷媒とする低温用レシプロ型圧縮機を流用して、蒸発温度−１０〜１０℃、凝縮温度６０〜８０℃の厳しい加温条件において圧縮機の耐久性確保と圧縮機の高効率化が容易に実現できる。 As described above, the present embodiment has a dedicated cooling and heating system for cooling and heating the hot / cold switching chamber separately from the cooling means for the cold dedicated chamber and the second cold dedicated chamber. As a cooling and heating system, it has a dedicated high-temperature reciprocating compressor using R600a as a refrigerant, an indoor condenser, an indoor evaporator, an outdoor condenser, an outdoor evaporator, and a three-way switching valve. By exchanging heat with the outdoor air using the designed outdoor evaporator, the compression ratio can be reduced while maintaining the high temperature condition of the evaporation temperature -10 to 10 ° C, and the reciprocating type for high temperature using R600a as the refrigerant. By using a compressor, a low-temperature reciprocating compressor using R134a produced in large quantities as a refrigerant can be diverted to a strict process of evaporation temperature -10 to 10 ° C and condensation temperature 60 to 80 ° C. Efficiency of durability ensuring a compressor of the compressor can be easily realized in conditions.
また、ホット／コールド切換室を冷却加温する場合、比較的蒸発温度が低く吸入ガス密度が小さい冷却運転時に高速運転し、比較的蒸発温度が高く吸入ガス密度が大きい加温運転時に低速運転することで、それぞれの運転条件でほぼ同等の冷却能力と加温能力が得られ冷却加温システムの圧縮機として過不足のない能力が実現できるとともに、特に凝縮温度が高く圧縮機の断続に伴う加温ロスが大きい加温時に略連続運転することでより効率化が図れる。 In addition, when the hot / cold switching chamber is cooled and heated, a high-speed operation is performed during a cooling operation with a relatively low evaporation temperature and a low intake gas density, and a low-speed operation is performed during a heating operation with a relatively high evaporation temperature and a high intake gas density. Therefore, almost the same cooling capacity and heating capacity can be obtained under each operating condition, and the capacity of the cooling and heating system can be achieved without excess or deficiency, and the condensing temperature is particularly high due to intermittent compressors. More efficiency can be achieved by operating substantially continuously during warming with a large temperature loss.
また、コールド専用室および第二のコールド専用室の冷却システムを別に設けることで、冷却システムの小能力化が図れ、結果として理論効率が高沸点冷媒であるＲ６００ａを用いることができる。 Further, by providing separate cooling systems for the cold dedicated chamber and the second cold dedicated chamber, it is possible to reduce the capacity of the cooling system, and as a result, it is possible to use R600a, which has a high boiling point refrigerant with theoretical efficiency.
（実施の形態２）
図２は本発明の実施の形態２の自動販売機の冷媒回路図、図３は同実施の形態の自動販売機の冷却加温システムの運転範囲を示す図である。なお、実施の形態１と同一の構成については同一番号を付して、詳細な説明は省略する。
(Embodiment 2)
FIG. 2 is a refrigerant circuit diagram of the vending machine according to the second embodiment of the present invention, and FIG. 3 is a diagram showing an operation range of the cooling and heating system of the vending machine according to the second embodiment. In addition, the same number is attached | subjected about the structure same as Embodiment 1, and detailed description is abbreviate | omitted.
図２に示すように、本発明の自動販売機は、ホット／コールド切換室１、コールド専用室２、第二のコールド専用室３からなる貯蔵室を備え、Ｒ６００ａを冷媒とし、高温用レシプロ型圧縮機２０、ホット／コールド切換室１内に設置された室内熱交換器３０、貯蔵室の外に設置された室外熱交換器３１、冷却時と加温時に冷媒流路を切換える四方切換弁３２、キャピラリチューブ３３からなり、ホット／コールド切換室１の冷却と加温を専用に行う冷却加温システムを有する。 As shown in FIG. 2, the vending machine according to the present invention includes a storage chamber composed of a hot / cold switching chamber 1, a cold dedicated chamber 2, and a second cold dedicated chamber 3, and uses R600a as a refrigerant, and a reciprocating type for high temperature. The compressor 20, the indoor heat exchanger 30 installed in the hot / cold switching chamber 1, the outdoor heat exchanger 31 installed outside the storage chamber, and the four-way switching valve 32 for switching the refrigerant flow path during cooling and heating. The cooling / heating system is composed of a capillary tube 33 and performs dedicated cooling and heating of the hot / cold switching chamber 1.
また、室内熱交換器３０と室外熱交換器３１は、ともに四方切換弁３２を切換えることによって冷媒の凝縮あるいは蒸発を行うフィンチューブ熱交換器であり、凝縮能力と着霜耐力をバランスさせた設計としている。 The indoor heat exchanger 30 and the outdoor heat exchanger 31 are both fin tube heat exchangers that condense or evaporate the refrigerant by switching the four-way switching valve 32, and are designed to balance the condensing capacity and the frosting resistance. It is said.
例えば、室内熱交換器３０は凝縮温度と吸込み空気温度との差が１０℃において１５０〜２００Ｗの加温能力を有しているとともに、蒸発温度と吸込み空気温度との差が１０℃において１５０〜２００Ｗの冷却能力を有している。 For example, the indoor heat exchanger 30 has a heating capability of 150 to 200 W when the difference between the condensation temperature and the intake air temperature is 10 ° C., and the difference between the evaporation temperature and the intake air temperature is 150 to 200 ° C. at 10 ° C. It has a cooling capacity of 200W.
また、キャピラリチューブ３３は加温と冷却の両方のモードで使用し通過する冷媒の圧力を低下して蒸発圧力を調整するものである。 The capillary tube 33 is used in both heating and cooling modes to adjust the evaporation pressure by reducing the pressure of the refrigerant passing therethrough.
ここで、図３に示すように、加温モードでの冷却加温システムの運転範囲である領域Ａと、冷却モードでの冷却加温システムの運転範囲である領域Ｂは、凝縮温度と蒸発温度との相関がほぼ同じである。すなわち、冷却モードでの運転範囲である領域Ｂよりも凝縮温度を上げた加温モードでは、冷却モードよりも高い蒸発温度となる領域Ａで運転することから、固定抵抗であるキャピラリチューブ３３は加温と冷却の両方のモードで使用することができる。 Here, as shown in FIG. 3, the region A which is the operating range of the cooling and heating system in the heating mode and the region B which is the operating range of the cooling and heating system in the cooling mode are the condensation temperature and the evaporation temperature. The correlation with is almost the same. That is, in the heating mode in which the condensation temperature is higher than that in the region B which is the operation range in the cooling mode, the operation is performed in the region A in which the evaporation temperature is higher than that in the cooling mode. Can be used in both warm and cool modes.
なお、図３において、ｐ１およびｐ２は高温用レシプロ型圧縮機２０の能力を可変した時に運転状態が変化する方向を示し、ｑ１およびｑ２は凝縮温度を可変した時に運転状態が変化する方向を示す。つまり、固定抵抗であるキャピラリチューブ３３を用いても、高温用レシプロ型圧縮機２０の能力を可変することにより、ある程度の蒸発温度の制御は可能である。例えば、加温モード中に蒸発温度が５℃以下にならないように高温用レシプロ型圧縮機２０の能力を可変すれば、蒸発器となる室外熱交換器３１における着霜の回避や結露の低減が実現できる。 In FIG. 3, p1 and p2 indicate directions in which the operating state changes when the capacity of the high-temperature reciprocating compressor 20 is changed, and q1 and q2 indicate directions in which the operating state changes when the condensation temperature is changed. . That is, even when the capillary tube 33 having a fixed resistance is used, the evaporation temperature can be controlled to some extent by changing the capability of the high-temperature reciprocating compressor 20. For example, if the capacity of the high-temperature reciprocating compressor 20 is varied so that the evaporation temperature does not become 5 ° C. or lower during the heating mode, frost formation in the outdoor heat exchanger 31 serving as an evaporator can be avoided and condensation can be reduced. realizable.
以上のように構成された実施の形態２の自動販売機について、以下その動作を説明する。 The operation of the vending machine according to the second embodiment configured as described above will be described below.
ホット／コールド切換室１を冷却する場合、四方切換弁３２を冷却側に切換えて高温用レシプロ型圧縮機２０を駆動する。高温用レシプロ型圧縮機２０から吐出された冷媒は、四方切換弁３２を経由して室外熱交換器３１で凝縮された後、キャピラリチューブ３３で減圧されて、室内熱交換器３０へ供給される。そして、室内熱交換器３０で蒸発した冷媒が高温用レシプロ型圧縮機２０へ還流する。 When the hot / cold switching chamber 1 is cooled, the four-way switching valve 32 is switched to the cooling side to drive the high temperature reciprocating compressor 20. The refrigerant discharged from the high-temperature reciprocating compressor 20 is condensed in the outdoor heat exchanger 31 via the four-way switching valve 32, then depressurized in the capillary tube 33, and supplied to the indoor heat exchanger 30. . Then, the refrigerant evaporated in the indoor heat exchanger 30 returns to the high-temperature reciprocating compressor 20.
このとき、ホット／コールド切換室１が所定の温度に近づくと高温用レシプロ型圧縮機２０を減速して能力を低下することにより、蒸発温度を上げて冷却効率を向上する。例えば外気温度１５℃の安定運転条件ではホット／コールド切換室１の安定時の熱負荷は１００〜２００Ｗ程度であるので、高温用レシプロ型圧縮機２０は蒸発温度−２０〜−１５℃、凝縮温度３０〜４０℃の運転条件で５８〜７２ｒｐｓの高回転で略連続運転するように制御される。そして、ホット／コールド切換室１が所定の温度に達すると高温用レシプロ型圧縮機２０の運転を停止する。 At this time, when the hot / cold switching chamber 1 approaches a predetermined temperature, the high-temperature reciprocating compressor 20 is decelerated to reduce the capacity, thereby raising the evaporation temperature and improving the cooling efficiency. For example, under stable operating conditions with an outside air temperature of 15 ° C., the heat load when the hot / cold switching chamber 1 is stable is about 100 to 200 W, so the high-temperature reciprocating compressor 20 has an evaporation temperature of −20 to −15 ° C., a condensation temperature. It is controlled to operate substantially continuously at a high speed of 58 to 72 rps under an operating condition of 30 to 40 ° C. When the hot / cold switching chamber 1 reaches a predetermined temperature, the operation of the high-temperature reciprocating compressor 20 is stopped.
また、例えば外気温度１５℃でプルダウンする場合は、ホット／コールド切換室１の温度が高いために室内熱交換器３０の蒸発温度が上昇して冷却能力が増大する、すなわち能力の自動調整機能が働くことから、プルダウン時は高温用レシプロ型圧縮機２０を高回転で連続運転して、蒸発温度−１０℃、凝縮温度５０℃の高能力運転条件となるが、ホット／コールド切換室１の温度低下に従い前記した安定運転条件へ自動的に移行していく。 For example, when pulling down at an outside air temperature of 15 ° C., the temperature of the hot / cold switching chamber 1 is high, so that the evaporation temperature of the indoor heat exchanger 30 rises and the cooling capacity increases. Since it works, the reciprocating compressor 20 for high temperature is continuously operated at a high speed at the time of pull-down, resulting in high-capacity operating conditions of an evaporation temperature of −10 ° C. and a condensation temperature of 50 ° C., but the temperature of the hot / cold switching chamber 1 The system automatically shifts to the above-mentioned stable operation condition as it decreases.
一方、ホット／コールド切換室１を加温する場合、四方切換弁３２を加温側に切換えて高温用レシプロ型圧縮機２０を駆動する。高温用レシプロ型圧縮機２０から吐出された冷媒は、四方切換弁３２を経由して室内熱交換器３０で凝縮された後、キャピラリチューブ３３で減圧されて、室外熱交換器３１へ供給される。そして、室外熱交換器３１で蒸発した冷媒が高温用レシプロ型圧縮機２０へ還流する。 On the other hand, when the hot / cold switching chamber 1 is heated, the four-way switching valve 32 is switched to the heating side to drive the high-temperature reciprocating compressor 20. The refrigerant discharged from the high-temperature reciprocating compressor 20 is condensed in the indoor heat exchanger 30 via the four-way switching valve 32, then depressurized in the capillary tube 33, and supplied to the outdoor heat exchanger 31. . Then, the refrigerant evaporated in the outdoor heat exchanger 31 is returned to the high-temperature reciprocating compressor 20.
このとき、例えば外気温度１５℃ではホット／コールド切換室１の安定時の熱負荷は１００〜２００Ｗ程度であるので、高温用レシプロ型圧縮機２０は蒸発温度５〜１０℃、凝縮温度５５〜６５℃の運転条件で２７〜３５ｒｐｓの低回転で連続運転するように制御される。これは、より高い回転数で運転した場合、能力過剰となり室内熱交換器３０の凝縮温度が高温用レシプロ圧縮機２０の限界を越えて上昇し、耐久性の低下を招くとともに、高温用レシプロ圧縮機２０を断続運転する必要が生じ、停止状態から室内熱交換器３０の温度が所定温度に達するまでの無駄な運転が生じて全体として効率の低下を招く。 At this time, for example, when the outside air temperature is 15 ° C., the stable heat load of the hot / cold switching chamber 1 is about 100 to 200 W, so the high-temperature reciprocating compressor 20 has an evaporation temperature of 5 to 10 ° C. and a condensation temperature of 55 to 65. It is controlled so as to continuously operate at a low rotation of 27 to 35 rps under operating conditions of ° C. This is because when the engine is operated at a higher rotational speed, the capacity becomes excessive and the condensation temperature of the indoor heat exchanger 30 rises beyond the limit of the high-temperature reciprocating compressor 20, leading to a decrease in durability and high-temperature reciprocating compression. The machine 20 needs to be intermittently operated, and a wasteful operation occurs from the stop state until the temperature of the indoor heat exchanger 30 reaches a predetermined temperature, resulting in a decrease in efficiency as a whole.
また、例えば外気温度１５℃でプルアップする場合は、ホット／コールド切換室１を通常４００Ｗ程度で加温する必要がある。この場合、高温用レシプロ圧縮機２０は蒸発温度＋０〜＋５℃、凝縮温度７０〜７５℃の運転条件で７２ｒｐｓの高回転で連続運転するように制御される。ここで、重要な点は、プルダウンする場合に見られる能力の自動調整機構がプルアップする場合には働かず、高温用レシプロ圧縮機２０の能力が過剰に大きい時には室内熱交換器３０の凝縮温度が高くなり、さらに加温能力が増加する傾向があるとともに、ホット／コールド切換室１の温度が低い時には凝縮温度が低くなり、逆に加温能力が低下する傾向があるために、加温能力を高める制御が不可欠となる点である。本実施例においては、高温用レシプロ圧縮機２０の表面での無駄な放熱を抑制するためにコンプファン２８を停止するとともに、室内熱交換器３０に取り付けられた補助ヒータ（図示せず）をプルアップ初期に通電して凝縮温度を７０〜７５℃に維持することが望ましい。 For example, when pulling up at an outside air temperature of 15 ° C., it is necessary to heat the hot / cold switching chamber 1 at about 400 W. In this case, the high-temperature reciprocating compressor 20 is controlled so as to continuously operate at a high rotation speed of 72 rps under operating conditions of an evaporation temperature of +0 to + 5 ° C. and a condensation temperature of 70 to 75 ° C. Here, the important point is that the automatic adjustment mechanism of the capacity seen when pulling down does not work when pulling up, and when the capacity of the high-temperature reciprocating compressor 20 is excessively large, the condensation temperature of the indoor heat exchanger 30 The heating capacity tends to increase and the heating capacity tends to increase. When the temperature of the hot / cold switching chamber 1 is low, the condensation temperature decreases, and conversely, the heating capacity tends to decrease. It is a point that control to increase the is indispensable. In this embodiment, the comp fan 28 is stopped to suppress wasteful heat dissipation on the surface of the high-temperature reciprocating compressor 20 and an auxiliary heater (not shown) attached to the indoor heat exchanger 30 is pulled. It is desirable to maintain the condensing temperature at 70 to 75 ° C by energizing in the initial stage of up.
従って、本実施例の構成において効率よくホット／コールド切換室１の冷却と加温を実現するには、プルダウン中は高温用レシプロ圧縮機２０の回転数を比較的高回転で維持すればよいが、プルアップ中にはホット／コールド切換室１内の温度が上昇するに伴って、高温用レシプロ圧縮機２０の回転数を２７〜３５ｒｐｓまで順次低下させて能力調整する必要がある。また、ホット／コールド切換室１内の温度が上昇する過程で、凝縮温度が高温用レシプロ圧縮機２０の限界を越えないように、望ましくは、室内熱交換器３０の凝縮温度を検知する温度センサーを設けるとともに、室内熱交換器３０の凝縮温度が所定値を越えると高温用レシプロ圧縮機２０の回転数を下げる制御を行う方がよい。 Accordingly, in order to efficiently cool and warm the hot / cold switching chamber 1 in the configuration of the present embodiment, the rotational speed of the high-temperature reciprocating compressor 20 may be maintained at a relatively high speed during pull-down. During the pull-up, as the temperature in the hot / cold switching chamber 1 rises, it is necessary to adjust the capacity by sequentially decreasing the rotational speed of the high-temperature reciprocating compressor 20 to 27 to 35 rps. Preferably, the temperature sensor detects the condensation temperature of the indoor heat exchanger 30 so that the condensation temperature does not exceed the limit of the high-temperature reciprocating compressor 20 in the process of increasing the temperature in the hot / cold switching chamber 1. In addition, when the condensation temperature of the indoor heat exchanger 30 exceeds a predetermined value, it is preferable to perform control to reduce the rotational speed of the high-temperature reciprocating compressor 20.
なお、本実施の形態においては、１５℃における冷却安定時のホット／コールド切換室１の冷却負荷を１００〜２００Ｗ程度、加温安定時のホット／コールド切換室１の加温負荷を１００〜２００Ｗ程度である標準的な自動販売機を想定したが、他の自動販売機においても１５〜２５℃の常温付近では冷却負荷と加温負荷はほぼ同程度であるとともに、加温時に比べて冷却時の蒸発温度が低いことから、加温安定時の過剰な加温能力を抑制するために高温用レシプロ型圧縮機２０の能力を低減する必要がある点に変わりはない。 In the present embodiment, the cooling load of the hot / cold switching chamber 1 when cooling is stable at 15 ° C. is about 100 to 200 W, and the heating load of the hot / cold switching chamber 1 when heating is stable is 100 to 200 W. A standard vending machine is assumed, but in other vending machines, the cooling load and the heating load are approximately the same at around 15 to 25 ° C, and the cooling time is lower than the heating time. Since the evaporation temperature is low, there is no change in that it is necessary to reduce the capacity of the high-temperature reciprocating compressor 20 in order to suppress excessive warming capacity during stable heating.
なお、本実施の形態においては、ホット／コールド切換室１の加温時のプルアップを補助ヒータと冷却加温システムの両方で実現したが、補助ヒータだけを用いてプルアップを行い、ホット／コールド切換室１の温度が安定した時点で冷却加温システムの加温能力で保温しても、保温時の加温効率改善は実現できる。 In this embodiment, the hot / cold switching chamber 1 is pulled up by heating with both the auxiliary heater and the cooling / heating system. Even when the temperature of the cold switching chamber 1 is stabilized and the temperature is maintained with the heating capability of the cooling and heating system, the heating efficiency can be improved when the temperature is maintained.
なお、本実施の形態においては、キャピラリチューブ３３と高温用レシプロ型圧縮機２０の吸入配管との熱交換を行わなかったが、室内熱交換器３０と四方切換弁３２を接続する配管あるいは四方切換弁３２と高温用レシプロ型圧縮機２０を接続する配管と、キャピラリチューブ３３を熱交換して冷却加温システムの冷却能力を向上することができる。 In the present embodiment, heat exchange between the capillary tube 33 and the suction pipe of the high-temperature reciprocating compressor 20 is not performed, but a pipe connecting the indoor heat exchanger 30 and the four-way switching valve 32 or four-way switching is performed. The cooling capacity of the cooling and heating system can be improved by exchanging heat between the piping connecting the valve 32 and the high-temperature reciprocating compressor 20 and the capillary tube 33.
なお、本実施の形態においては、冷却加温システムの固定抵抗としてキャピラリチューブ３３を用いたが、電動膨張弁のような可変抵抗を用いてもよい。可変抵抗を用いた場合、凝縮温度が上がりにくいプルアップ時に可変抵抗を小さくすることで冷却加温システムのプルアップ特性を改善するとともに、補助ヒータの低入力化を図ることができる。 In this embodiment, the capillary tube 33 is used as the fixed resistance of the cooling and heating system, but a variable resistance such as an electric expansion valve may be used. When a variable resistor is used, it is possible to improve the pull-up characteristic of the cooling and heating system by reducing the variable resistor at the time of pull-up when it is difficult to raise the condensation temperature, and to reduce the input of the auxiliary heater.
なお、本実施の形態においては、ホット／コールド切換室１を加温する場合の室外熱交換器３１の蒸発温度を０〜１０℃の効率の高い範囲で任意に調整したが、特に自動販売機が室内に設置されて結露水が排出できない場合は、結露しない範囲でのみ冷却加温システムを稼動し、雨天などの高湿度条件では補助ヒータのみによる加温に切換えることが望ましい。 In the present embodiment, the evaporation temperature of the outdoor heat exchanger 31 when the hot / cold switching chamber 1 is heated is arbitrarily adjusted within a high efficiency range of 0 to 10 ° C. If the dew condensation water cannot be discharged because it is installed indoors, it is desirable to operate the cooling and heating system only within the range where condensation does not occur, and to switch to heating only with an auxiliary heater under high humidity conditions such as rainy weather.
以上のように、本実施の形態においては、コールド専用室２および第二のコールド専用室３の冷却手段とは別に、ホット／コールド切換室１を冷却加温する専用の冷却加温システムを有するとともに、この冷却加温システムとして、Ｒ６００ａを冷媒とする高温用レシプロ型圧縮機２０と、室内熱交換器３０と、室外熱交換器３１と、四方切換弁３２と、キャピラリチューブを備えたことによって、部品点数の少ない安価な構成で室外の大気と熱交換することで、蒸発温度−１０〜１０℃の高温条件に維持して圧縮比を低減することができるとともに、Ｒ６００ａを冷媒とする高温用レシプロ型圧縮機２０を用いることで、大量に生産されているＲ１３４ａを冷媒とする低温用レシプロ型圧縮機を流用して、蒸発温度−１０〜１０℃、凝縮温度６０〜８０℃の厳しい加温条件において圧縮機の耐久性確保と圧縮機の高効率化が容易に実現できる。 As described above, the present embodiment has a dedicated cooling and heating system for cooling and heating the hot / cold switching chamber 1 separately from the cooling means for the cold dedicated chamber 2 and the second cold dedicated chamber 3. In addition, the cooling and heating system includes a high-temperature reciprocating compressor 20 using R600a as a refrigerant, an indoor heat exchanger 30, an outdoor heat exchanger 31, a four-way switching valve 32, and a capillary tube. By exchanging heat with the outdoor air in an inexpensive configuration with a small number of parts, the compression ratio can be reduced while maintaining the high temperature condition of the evaporation temperature −10 to 10 ° C., and for high temperature using R600a as a refrigerant By using the reciprocating compressor 20, a low temperature reciprocating compressor using R134a produced in large quantities as a refrigerant is diverted to an evaporation temperature of −10 to 10 ° C., a condensation temperature. High efficiency of the compressor and secure durability of the compressor under severe heating conditions 60-80 ° C. can be easily realized.
また、ホット／コールド切換室１を冷却加温する場合、比較的蒸発温度が低く吸入ガス密度が小さい冷却運転時に高速運転し、比較的蒸発温度が高く吸入ガス密度が大きい加温運転時に低速運転することで、それぞれの運転条件でほぼ同等の冷却能力と加温能力が得られ冷却加温システムの圧縮機として過不足のない能力が実現できるとともに、特に凝縮温度が高く圧縮機の断続に伴う加温ロスが大きい加温時に略連続運転することでより効率化が図れる。 Further, when the hot / cold switching chamber 1 is cooled and heated, a high-speed operation is performed during a cooling operation with a relatively low evaporation temperature and a low intake gas density, and a low-speed operation is performed during a heating operation with a relatively high evaporation temperature and a high intake gas density. As a result, almost the same cooling capacity and heating capacity can be obtained under each operating condition, so that the capacity of the cooling and heating system can be achieved without excess or deficiency, and the condensation temperature is particularly high due to intermittent compressors. More efficiency can be achieved by performing a substantially continuous operation during heating with a large heating loss.
また、コールド専用室２および第二のコールド専用室３の冷却システムを別に設けることで、冷却システムの小能力化が図れ、結果として理論効率が高沸点冷媒であるＲ６００ａを用いることができる。 Further, by providing separate cooling systems for the cold dedicated chamber 2 and the second cold dedicated chamber 3, the cooling system can be reduced in capacity, and as a result, R600a having a high boiling point refrigerant can be used.
以上のように、本発明にかかる自動販売機の冷却加温システムは、Ｒ６００ａを冷媒とする高温用レシプロ型圧縮機を用いることで、蒸発温度−１０〜１０℃、凝縮温度６０〜８０℃の厳しい加温条件において小能力でかつ高効率な加温システムが容易に実現できるとともに、比較的蒸発温度が低く吸入ガス密度が小さい冷却運転時に高速運転し、比較的蒸発温度が高く吸入ガス密度が大きい加温運転時に低速運転することで、それぞれの運転条件でほぼ同等の冷却能力と加温能力が得られ冷却加温システムの圧縮機として過不足のない能力が実現できるとともに、特に凝縮温度が高く圧縮機の断続に伴う加温ロスが大きい加温時に略連続運転することでより効率化が図れるので、ホット飲料とコールド飲料を切換えて保存するショーケースや少量の給湯を行うカップ自販機など小能力の加温および冷却時の省エネルギー化が要求される用途にも適用できる。 As described above, the cooling and heating system of the vending machine according to the present invention uses an evaporating temperature of −10 to 10 ° C. and a condensation temperature of 60 to 80 ° C. by using a high-temperature reciprocating compressor using R600a as a refrigerant. A low-capacity and high-efficiency heating system can be easily realized under severe heating conditions, and at high speed during cooling operation with a relatively low evaporation temperature and a low intake gas density, the evaporation temperature is relatively high and the intake gas density is low. By operating at low speed during large warming operation, almost the same cooling capacity and warming capacity can be obtained under each operating condition. Showcase that switches between hot and cold beverages because it is more efficient by operating almost continuously during warming with high heating loss due to intermittent compressors. It can be applied to applications where a small amount of energy saving during heating and cooling of small capacity such as a cup vending machines to perform hot-water supply is required.
１ ホット／コールド切換室
２ コールド専用室
３ 第二のコールド専用室
２０ 高温用レシプロ型圧縮機（圧縮機）
２１ 室内蒸発器
２２ 室内凝縮器
２３ 室外蒸発器
２４ 室外凝縮器
２５ 三方切換弁
３０ 室内熱交換器
３１ 室外熱交換器
３２ 四方切換弁
1 Hot / cold switching room 2 Cold dedicated room 3 Second cold dedicated room 20 High temperature reciprocating compressor (compressor)
DESCRIPTION OF SYMBOLS 21 Indoor evaporator 22 Indoor condenser 23 Outdoor evaporator 24 Outdoor condenser 25 Three-way switching valve 30 Indoor heat exchanger 31 Outdoor heat exchanger 32 Four-way switching valve
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| JP2007274997A JP4155335B2 (en) | 2007-10-23 | 2007-10-23 | vending machine |
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| Application Number | Priority Date | Filing Date | Title |
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| JP2007274997A JP4155335B2 (en) | 2007-10-23 | 2007-10-23 | vending machine |
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| JP2004211321A Division JP4513441B2 (en) | 2004-07-01 | 2004-07-20 | Vending machine with cooling and heating system |
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| JP2008052751A true JP2008052751A (en) | 2008-03-06 |
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