JP2010060159A - Refrigerating device - Google Patents

Refrigerating device Download PDF

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JP2010060159A
JP2010060159A JP2008223837A JP2008223837A JP2010060159A JP 2010060159 A JP2010060159 A JP 2010060159A JP 2008223837 A JP2008223837 A JP 2008223837A JP 2008223837 A JP2008223837 A JP 2008223837A JP 2010060159 A JP2010060159 A JP 2010060159A
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heat exchanger
refrigerant
fins
evaporator
fin
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Takayuki Setoguchi
隆之 瀬戸口
Koji Shibaike
幸治 芝池
Takahiro Okamoto
高宏 岡本
Tomoyuki Haikawa
知之 配川
Yoichi Onuma
洋一 大沼
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Daikin Industries Ltd
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Daikin Industries Ltd
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Abstract

<P>PROBLEM TO BE SOLVED: To suppress frost formation on an evaporator by a comparatively inexpensive method to suppress degradation of operational efficiency caused by frost formation, in a refrigerating device using a zeotropic refrigerant mixture including a refrigerant composed of an organic compound represented by a formula C<SB>3</SB>H<SB>m</SB>F<SB>n</SB>(m=1-5, n=1-5, m+n=6), and having one double bond in a molecular structure. <P>SOLUTION: An air conditioner 1 applies the refrigerating device using the zeotropic refrigerant mixture (R1234+R32), and comprises an outdoor heat exchanger 30 used as the evaporator in a heating operation. The outdoor heat exchanger 30 has a first heat exchanger 31 and a second heat exchanger 32, and the first heat exchanger 31 is positioned at a refrigerant inlet side. Frost formation preventing treatment for forming a water-repellent coating film is performed only on a first fin 111 of the first heat exchanger 31. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、冷凍装置、特に、非共沸混合冷媒を用いる冷凍装置に関する。   The present invention relates to a refrigeration apparatus, and more particularly to a refrigeration apparatus that uses a non-azeotropic refrigerant mixture.

近年、環境保護の観点から、冷凍装置に使用される冷媒として、地球温暖化係数（ＧＷＰ）の低い冷媒（以後、低ＧＷＰ冷媒とよぶ）が検討されている。低ＧＷＰ冷媒としては、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒が有力である。 In recent years, from the viewpoint of environmental protection, a refrigerant having a low global warming potential (GWP) (hereinafter referred to as a low GWP refrigerant) has been studied as a refrigerant used in a refrigeration apparatus. The low GWP refrigerant, the molecular formula C 3 H m F n (where, m = 1~5, n = 1~5 , and m + n = 6) organic having the single double bond in and molecular structure represented by Non-azeotropic refrigerant mixtures including refrigerants composed of compounds are promising.

しかしながら、非共沸混合冷媒を使用した冷凍装置は、単一冷媒を使用した冷凍装置と異なり、蒸発器の入口付近の温度が低くなるので、蒸発器の入口付近が着霜し易く、頻繁に除霜運転となって運転効率が低下する可能性が高い。着霜防止手段として、蒸発器に撥水性処理を施したフィン（例えば、特許文献１参照）を搭載することがあるが、フィン全体に処理を施すため、製造コスト増大の要因になっている。
特開昭６３−３１８２号公報 However, unlike a refrigeration system that uses a single refrigerant, a refrigeration system that uses a non-azeotropic refrigerant mixture has a lower temperature near the inlet of the evaporator, so it tends to frost around the inlet of the evaporator and frequently There is a high possibility that the defrosting operation results in a decrease in operating efficiency. As an anti-frosting means, fins subjected to water repellency treatment (for example, see Patent Document 1) may be mounted on the evaporator. However, since the entire fin is treated, it causes an increase in manufacturing cost.
JP-A-63-3182

本発明の課題は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を使用する冷凍装置において、比較的安価な方法で蒸発器の着霜を抑制し、着霜による運転効率の低下を抑制することにある。 An object of the present invention is an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure. In a refrigeration apparatus using a non-azeotropic refrigerant mixture including a refrigerant composed of a compound, the frost formation of the evaporator is suppressed by a relatively inexpensive method, and the decrease in operation efficiency due to the frost formation is suppressed.

第１発明に係る冷凍装置は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、複数のフィンを有する蒸発器を備えている。複数のフィンのうち蒸発器の冷媒入口近傍に位置するフィンのみに、着霜を防止するための着霜防止処理が施されている。 In the refrigeration apparatus according to the first invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and a double bond is 1 in the molecular structure. A refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound, and includes an evaporator having a plurality of fins. Only the fin located in the vicinity of the refrigerant inlet of the evaporator among the plurality of fins is subjected to a frost prevention process for preventing frost formation.

非共沸混合冷媒の場合、蒸発器の冷媒入口近傍が最も温度が低く着霜し易い部分であるが、この冷凍装置では、着霜し易い部分に着霜防止処理が施されているので着霜し難くなる。その結果、運転時間が長く維持され、運転効率が向上する。また、フィン全体に着霜防止処理を施す必要がないので、コスト増大が抑制される。   In the case of a non-azeotropic refrigerant mixture, the vicinity of the refrigerant inlet of the evaporator is the portion where the temperature is lowest and is likely to be frosted. It becomes difficult to frost. As a result, the operation time is maintained longer and the operation efficiency is improved. Moreover, since it is not necessary to perform the frost formation prevention process to the whole fin, an increase in cost is suppressed.

第２発明に係る冷凍装置は、第１発明に係る冷凍装置であって、蒸発器が、冷媒の入口側に位置する第１熱交換器と、第１熱交換器を通過した冷媒が流れる第２熱交換器とを含んでいる。複数のフィンのうち第１熱交換器側のフィンのみに着霜防止処理が施されている。   A refrigeration apparatus according to a second aspect of the present invention is the refrigeration apparatus according to the first aspect of the present invention, wherein the evaporator includes a first heat exchanger located on the refrigerant inlet side, and a refrigerant through which the refrigerant having passed through the first heat exchanger flows. 2 heat exchangers. Of the plurality of fins, only the fin on the first heat exchanger side is subjected to frosting prevention processing.

この冷凍装置では、最も温度が低く着霜し易い第１熱交換器に着霜防止処理が施されているので、着霜し難くなり運転時間が長く維持される。   In this refrigeration system, since the first heat exchanger with the lowest temperature and easy frost formation is subjected to the frost prevention treatment, frost formation is difficult and the operation time is maintained for a long time.

第３発明に係る冷凍装置は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、複数のフィンを有する蒸発器を備えている。複数のフィンのうち蒸発器の液冷媒が存在する領域に位置するフィンのみに、着霜を防止するための着霜防止処理が施されている。 In the refrigeration apparatus according to the third aspect of the present invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and 1 double bond is present in the molecular structure. A refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound, and includes an evaporator having a plurality of fins. Only the fin located in the area | region where the liquid refrigerant of an evaporator exists among several fins is subjected to the frost prevention process for preventing frost formation.

非共沸混合冷媒の場合、蒸発器の液冷媒が存在する領域が最も温度が低く着霜し易い部分であるが、この冷凍装置では、着霜し易い部分に着霜防止処理が施されているので、着霜し難くなる。その結果、運転時間が長く維持され、運転効率が向上する。また、フィン全体に着霜防止処理を施す必要がないので、コスト増大が抑制される。   In the case of a non-azeotropic refrigerant mixture, the region where the liquid refrigerant of the evaporator exists is the portion where the temperature is the lowest and is likely to form frost, but in this refrigeration apparatus, the portion that is likely to form frost is subjected to frost prevention treatment. Because it is difficult to frost. As a result, the operation time is maintained longer and the operation efficiency is improved. Moreover, since it is not necessary to perform the frost formation prevention process to the whole fin, an increase in cost is suppressed.

第４発明に係る冷凍装置は、第３発明に係る冷凍装置であって、フィンが、液側フィンとガス側フィンとに分割されている。液側フィンは、蒸発器の液冷媒が存在する領域に位置する。ガス側フィンは、蒸発器のガス冷媒が存在する領域に位置する。そして、液側フィンのみに着霜防止処理が施されている。この冷凍装置では、フィン全体に着霜防止処理を施したものと比較して、製造コストが低い。   A refrigeration apparatus according to a fourth aspect is the refrigeration apparatus according to the third aspect, wherein the fin is divided into a liquid side fin and a gas side fin. A liquid side fin is located in the area | region where the liquid refrigerant of an evaporator exists. The gas side fin is located in a region where the gas refrigerant of the evaporator exists. And only the liquid side fin is subjected to the frost prevention treatment. In this refrigeration apparatus, the manufacturing cost is lower than that in which the entire fin is subjected to a frost prevention treatment.

第５発明に係る冷凍装置は、第１発明から第４発明のいずれか１つに係る冷凍装置であって、着霜防止処理が、親水性の被膜を形成する処理である。この冷凍装置では、親水性の被膜上の結露水は広がり易くなる反面、降下する速度が早くなる。その結果、結露水が素早く落下するので、氷結する水滴が減少し着霜量も減少する。   A refrigeration apparatus according to a fifth aspect of the present invention is the refrigeration apparatus according to any one of the first to fourth aspects of the present invention, wherein the frost prevention treatment is a treatment for forming a hydrophilic film. In this refrigeration apparatus, the condensed water on the hydrophilic film is likely to spread, but the rate of descending is faster. As a result, the condensed water quickly drops, so that water droplets that freeze are reduced and the amount of frost formation is also reduced.

第６発明に係る冷凍装置は、第１発明から第４発明のいずれか１つに係る冷凍装置であって、着霜防止処理が、撥水性の被膜を形成する処理である。この冷凍装置では、結露水は撥水性の被膜に弾かれて落下するので、氷結する水滴が減少し着霜量も減少する。   The refrigeration apparatus according to a sixth aspect of the present invention is the refrigeration apparatus according to any one of the first to fourth aspects of the present invention, wherein the frosting prevention process is a process for forming a water-repellent film. In this refrigeration apparatus, the condensed water is bounced by the water-repellent film and falls, so that water droplets that freeze are reduced and the amount of frost formation is also reduced.

第７発明に係る冷凍装置は、第１発明から第４発明のいずれか１つに係る冷凍装置であって、着霜防止処理が、滑水性の被膜を形成する処理である。この冷凍装置では、滑水性の被膜上の結露水は空気流及び重力の作用によって容易に落下するので、氷結する水滴が減少し着霜量も減少する（例えば、特許文献１参照）。   The refrigeration apparatus according to a seventh aspect of the present invention is the refrigeration apparatus according to any one of the first to fourth aspects of the present invention, wherein the frosting prevention process is a process for forming a sliding film. In this refrigeration apparatus, the condensed water on the water-slidable film easily falls due to the action of air flow and gravity, so that water droplets that freeze are reduced and the amount of frost formation is also reduced (see, for example, Patent Document 1).

第８発明に係る冷凍装置は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、複数のフィンを有する蒸発器を備えている。複数のフィンのうち蒸発器の冷媒入口近傍に位置するフィン同士の間隔が、冷媒入口近傍に位置しないフィン同士の間隔よりも大きい。 In the refrigeration apparatus according to the eighth aspect of the invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and one double bond is present in the molecular structure. A refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound, and includes an evaporator having a plurality of fins. The space | interval of the fins located near the refrigerant | coolant inlet_port | entrance of an evaporator among several fins is larger than the space | interval of fins not located in the refrigerant | coolant inlet vicinity.

非共沸混合冷媒の場合、蒸発器の冷媒入口近傍が最も温度が低く着霜し易い部分であるが、この冷凍装置では、着霜し易い部分のフィン同士の間隔が大きく設定されているので通風抵抗が低下する。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In the case of a non-azeotropic refrigerant mixture, the vicinity of the refrigerant inlet of the evaporator is the portion where the temperature is the lowest and is likely to form frost, but in this refrigeration apparatus, the interval between the fins in the portion that tends to form frost is set large. Ventilation resistance decreases. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第９発明に係る冷凍装置は、第８発明に係る冷凍装置であって、蒸発器が、冷媒の入口側に位置する第１熱交換器と第１熱交換器を通過した冷媒が流れる第２熱交換器とを含んでいる。複数のフィンのうち第１熱交換器側のフィン同士の間隔が、第２熱交換器側のフィン同士の間隔よりも大きい。   A refrigeration apparatus according to a ninth aspect of the present invention is the refrigeration apparatus according to the eighth aspect of the present invention, wherein the evaporator has a first heat exchanger located on the refrigerant inlet side and a refrigerant that has passed through the first heat exchanger flows through the second refrigeration apparatus. Includes heat exchanger. The space | interval of the fins by the side of the 1st heat exchanger among several fins is larger than the space | interval of the fins by the side of the 2nd heat exchanger.

この冷凍装置では、最も温度が低く着霜し易い第１熱交換器のフィン同士の間隔が大きく設定されているので、第１熱交換器の通風抵抗が低下する。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In this refrigeration apparatus, since the interval between the fins of the first heat exchanger that is the lowest temperature and easily frosts is set large, the ventilation resistance of the first heat exchanger is reduced. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第１０発明に係る冷凍装置は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、複数のフィンを有する蒸発器を備えている。複数のフィンのうち蒸発器の液冷媒が存在する領域に位置するフィン同士の間隔が、その領域に位置しないフィン同士の間隔よりも大きい。 In the refrigeration apparatus according to the tenth aspect of the invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and one double bond is present in the molecular structure. A refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound, and includes an evaporator having a plurality of fins. The space | interval of the fins located in the area | region where the liquid refrigerant of an evaporator exists among several fins is larger than the space | interval of the fins which are not located in the area | region.

非共沸混合冷媒の場合、蒸発器の液冷媒が存在する領域が最も温度が低く着霜し易い部分であるが、この冷凍装置では、着霜し易い部分のフィン同士の間隔が大きく設定されているので通風抵抗が低下する。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In the case of a non-azeotropic refrigerant mixture, the region where the liquid refrigerant of the evaporator exists is the portion where the temperature is lowest and is likely to be frosted. As a result, the draft resistance decreases. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第１１発明に係る冷凍装置は、第１０発明に係る冷凍装置であって、フィンが、液側フィンとガス側フィンとに分割されている。液側フィンは、蒸発器の液冷媒が存在する領域に位置する。ガス側フィンは、蒸発器のガス冷媒が存在する領域に位置する。液側フィン同士の間隔が、ガス側フィン同士の間隔よりも大きい。   A refrigeration apparatus according to an eleventh aspect of the invention is the refrigeration apparatus according to the tenth aspect of the invention, wherein the fin is divided into a liquid side fin and a gas side fin. A liquid side fin is located in the area | region where the liquid refrigerant of an evaporator exists. The gas side fin is located in a region where the gas refrigerant of the evaporator exists. The interval between the liquid side fins is larger than the interval between the gas side fins.

この冷凍装置では、蒸発器全域でフィン同士の間隔を大きくする必要はないので、蒸発器本来の熱交換性能が低下することはない。   In this refrigeration apparatus, it is not necessary to increase the distance between the fins in the entire evaporator, so that the original heat exchange performance of the evaporator does not deteriorate.

第１２発明に係る冷凍装置は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、複数のフィンを有する蒸発器を備えている。複数のフィンのうち蒸発器の冷媒入口近傍に位置するフィンは、冷媒入口近傍に位置しないフィンよりも通風抵抗が小さくなるフィン形状をしている。 In the refrigeration apparatus according to the twelfth aspect of the invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and one double bond is present in the molecular structure. A refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound, and includes an evaporator having a plurality of fins. Of the plurality of fins, the fin located near the refrigerant inlet of the evaporator has a fin shape in which the ventilation resistance is smaller than that of the fin not located near the refrigerant inlet.

非共沸混合冷媒の場合、蒸発器の冷媒入口近傍が最も温度が低く着霜し易い部分であるが、この冷凍装置では、着霜し易い部分のフィンは通風抵抗が小さくなるフィン形状をしている。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In the case of a non-azeotropic refrigerant mixture, the vicinity of the refrigerant inlet of the evaporator is the portion where the temperature is lowest and is likely to be frosted. ing. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第１３発明に係る冷凍装置は、第１２発明に係る冷凍装置であって、蒸発器が、冷媒の入口側に位置する第１熱交換器と第１熱交換器を通過した冷媒が流れる第２熱交換器とを含んでいる。複数のフィンのうち第１熱交換器側のフィンは、第２熱交換器側のフィンよりも通風抵抗が小さくなるフィン形状をしている。   A refrigeration apparatus according to a thirteenth aspect of the present invention is the refrigeration apparatus according to the twelfth aspect of the present invention, wherein the evaporator is a second heat source through which the refrigerant passing through the first heat exchanger and the first heat exchanger flows. Includes heat exchanger. Of the plurality of fins, the fin on the first heat exchanger side has a fin shape with lower ventilation resistance than the fin on the second heat exchanger side.

この冷凍装置では、最も温度が低く着霜し易い第１熱交換器のフィンが、通風抵抗が小さくなるフィン形状をしているので、第１熱交換器の通風抵抗が低下する。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In this refrigeration apparatus, the fins of the first heat exchanger that have the lowest temperature and are likely to be frosted have a fin shape in which the ventilation resistance is reduced, so the ventilation resistance of the first heat exchanger is reduced. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第１４発明に係る冷凍装置は、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、複数のフィンを有する蒸発器を備えている。複数のフィンのうち蒸発器の液冷媒が存在する領域に位置するフィンは、その領域に位置しないフィンよりも通風抵抗が小さくなるフィン形状をしている。 In the refrigeration apparatus according to the fourteenth aspect of the invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and one double bond is present in the molecular structure. A refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound, and includes an evaporator having a plurality of fins. The fin located in the area | region where the liquid refrigerant of an evaporator exists among several fins is carrying out the fin shape in which ventilation resistance becomes smaller than the fin which is not located in the area | region.

非共沸混合冷媒の場合、蒸発器の液冷媒が存在する領域が最も温度が低く着霜し易い部分であるが、この冷凍装置では、着霜し易い部分のフィンは通風抵抗が小さくなるフィン形状をしている。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In the case of a non-azeotropic refrigerant mixture, the region where the liquid refrigerant of the evaporator exists is the portion where the temperature is lowest and is likely to be frosted. It has a shape. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第１５発明に係る冷凍装置は、第１４発明に係る冷凍装置であって、フィンが、液側フィンとガス側フィンとに分割されている。液側フィンは、蒸発器の液冷媒が存在する領域に位置する。ガス側フィンは、蒸発器のガス冷媒が存在する領域に位置する。液側フィンは、ガス側フィンよりも通風抵抗が小さくなるフィン形状をしている。   A refrigeration apparatus according to a fifteenth aspect of the present invention is the refrigeration apparatus according to the fourteenth aspect of the present invention, wherein the fin is divided into a liquid side fin and a gas side fin. A liquid side fin is located in the area | region where the liquid refrigerant of an evaporator exists. The gas side fin is located in a region where the gas refrigerant of the evaporator exists. The liquid-side fin has a fin shape in which the ventilation resistance is smaller than that of the gas-side fin.

この冷凍装置では、元々着霜し難いガス側フィンには、切り起しなどの熱交換量を増加させるための形状を付加することができるので、蒸発器全体の熱交換性能が低下することはない。   In this refrigeration system, it is possible to add a shape for increasing the amount of heat exchange, such as cutting and raising, to the gas-side fins that are difficult to frost from the beginning, so that the heat exchange performance of the entire evaporator is not reduced. Absent.

第１６発明に係る冷凍装置は、第１２発明から第１５発明のいずれか１つに係る冷凍装置であって、フィン形状が、冷媒が流通する管との接触部を除いて切り起しのない平板状である。   A refrigeration apparatus according to a sixteenth aspect of the present invention is the refrigeration apparatus according to any one of the twelfth to fifteenth aspects of the present invention, wherein the fin shape does not cut up except for a contact portion with a pipe through which the refrigerant flows. It is flat.

この冷凍装置では、着霜し易い部分のフィンは通風抵抗が小さくなるフィン形状をしている。その結果、着霜し難くなり運転時間が長く維持され、運転効率が向上する。   In this refrigeration apparatus, the fins that are likely to be frosted have a fin shape with low ventilation resistance. As a result, it becomes difficult to form frost, the operation time is maintained for a long time, and the operation efficiency is improved.

第１７発明に係る冷凍装置は、第２発明、第９発明および第１３発明のいずれか１つに係る冷凍装置であって、第１熱交換器および第２熱交換器が凝縮器として機能する運転が行われたとき、第１熱交換器は、第２熱交換器を通過した冷媒を過冷却する補助熱交換器として機能する。   A refrigeration apparatus according to a seventeenth aspect of the present invention is the refrigeration apparatus according to any one of the second, ninth, and thirteenth aspects, wherein the first heat exchanger and the second heat exchanger function as a condenser. When the operation is performed, the first heat exchanger functions as an auxiliary heat exchanger that supercools the refrigerant that has passed through the second heat exchanger.

この冷凍装置では、第１熱交換器は、凝縮器として機能するときは過冷却冷媒を収容し、蒸発器として機能するときは着霜を防止する。   In this refrigeration apparatus, the first heat exchanger accommodates a supercooled refrigerant when functioning as a condenser, and prevents frost formation when functioning as an evaporator.

第１８発明に係る冷凍装置は、第２発明、第９発明および第１３発明のいずれか１つに係る冷凍装置であって、第２熱交換器は断面形状がほぼ逆Ｖ字状を成している。第１熱交換器は、第２熱交換器を通過する空気流の上流側に、第２熱交換器に沿って配置されている。   A refrigeration apparatus according to an eighteenth aspect of the present invention is the refrigeration apparatus according to any one of the second, ninth and thirteenth aspects of the invention, wherein the second heat exchanger has a substantially inverted V-shaped cross section. ing. The first heat exchanger is disposed along the second heat exchanger on the upstream side of the air flow passing through the second heat exchanger.

この冷凍装置では、空気調和装置の室内機に応用した場合、暖房運転時は過冷却冷媒を収容し、冷房運転時は着霜を防止する。   In this refrigeration apparatus, when applied to an indoor unit of an air conditioner, supercooled refrigerant is accommodated during heating operation and frost formation is prevented during cooling operation.

第１発明、又は第３発明に係る冷凍装置では、着霜し易い部分に着霜防止処理が施されているので着霜し難くなる。その結果、運転時間が長く維持され、運転効率が向上する。また、フィン全体に着霜防止処理を施す必要がないので、コスト増大が抑制される。   In the refrigeration apparatus according to the first invention or the third invention, frost formation is difficult to form because the frost prevention treatment is applied to the portion where frost formation easily occurs. As a result, the operation time is maintained longer and the operation efficiency is improved. Moreover, since it is not necessary to perform the frost formation prevention process to the whole fin, an increase in cost is suppressed.

第２発明に係る冷凍装置では、最も温度が低く着霜し易い第１熱交換器に着霜防止処理が施されているので、着霜し難くなり運転時間が長く維持される。   In the refrigeration apparatus according to the second aspect of the present invention, since the first heat exchanger with the lowest temperature and easy frost formation is subjected to the frost prevention treatment, frost formation is difficult and the operation time is maintained for a long time.

第４発明に係る冷凍装置では、フィン全体に着霜防止処理を施したものと比較して、製造コストが低い。   In the refrigeration apparatus according to the fourth aspect of the present invention, the manufacturing cost is lower than that in which the entire fin is subjected to the frost prevention treatment.

第５発明に係る冷凍装置では、親水性の被膜上の結露水は広がり易くなる反面、降下する速度が早くなる。その結果、結露水が素早く落下するので、氷結する水滴が減少し着霜量も減少する。   In the refrigeration apparatus according to the fifth aspect of the present invention, the condensed water on the hydrophilic film tends to spread, but the descending speed becomes faster. As a result, the condensed water quickly drops, so that water droplets that freeze are reduced and the amount of frost formation is also reduced.

第６発明に係る冷凍装置では、結露水は撥水性の被膜に弾かれて落下するので、氷結する水滴が減少し着霜量も減少する。   In the refrigeration apparatus according to the sixth aspect of the invention, the condensed water is bounced off by the water-repellent coating and falls, so that water droplets that freeze are reduced and the amount of frost formation is also reduced.

第７発明に係る冷凍装置では、滑水性の被膜上の結露水は空気流及び重力の作用によって容易に落下するので、氷結する水滴が減少し着霜量も減少する。   In the refrigeration apparatus according to the seventh aspect of the present invention, the dew condensation water on the water-slidable coating easily falls by the action of air flow and gravity, so that water droplets that freeze are reduced and the amount of frost formation is also reduced.

第８発明から第１０発明、第１２発明から第１４発明、および第１６発明のいずれか１つに係る冷凍装置では、着霜し難くなり運転時間が長く維持され、暖房運転効率が向上する。   In the refrigeration apparatus according to any one of the eighth to tenth inventions, the twelfth to fourteenth inventions, and the sixteenth invention, frost formation becomes difficult and the operation time is maintained longer, and the heating operation efficiency is improved.

第１１発明に係る冷凍装置では、蒸発器全域でフィン同士の間隔を大きくする必要はないので、蒸発器本来の熱交換性能が低下することはない。   In the refrigeration apparatus according to the eleventh aspect of the invention, it is not necessary to increase the distance between the fins throughout the evaporator, so that the original heat exchange performance of the evaporator does not deteriorate.

第１５発明に係る冷凍装置では、着霜し難いガス側フィンには、切り起しなどの熱交換量を増加させるための形状を付加することができるので、蒸発器全体の熱交換性能が低下することはない。   In the refrigeration apparatus according to the fifteenth aspect of the present invention, since the shape for increasing the heat exchange amount such as cutting and raising can be added to the gas-side fins that are difficult to form frost, the heat exchange performance of the entire evaporator is reduced. Never do.

第１７発明に係る冷凍装置では、第１熱交換器は、凝縮器として機能するときは過冷却冷媒を収容し、蒸発器として機能するときは着霜を防止する。   In the refrigeration apparatus according to the seventeenth aspect, the first heat exchanger accommodates the supercooled refrigerant when functioning as a condenser, and prevents frost formation when functioning as an evaporator.

第１８発明に係る冷凍装置では、空気調和装置の室内機に応用した場合、暖房運転時は過冷却冷媒を収容し、冷房運転時は着霜を防止する。   In the refrigeration apparatus according to the eighteenth aspect of the invention, when applied to an indoor unit of an air conditioner, supercooled refrigerant is accommodated during heating operation and frost formation is prevented during cooling operation.

以下図面を参照しながら、本発明の実施形態について説明する。なお、以下の実施形態は、本発明の具体例であって、本発明の技術的範囲を限定するものではない。   Embodiments of the present invention will be described below with reference to the drawings. The following embodiments are specific examples of the present invention and do not limit the technical scope of the present invention.

〔第１実施形態〕
＜空調機の構成＞
図１は、本発明の第１実施形態に係る冷凍装置を用いた空調機の構成図である。図１において、空調機１は、室外ユニット２と室内ユニット３とを備えている。なお、室内ユニット３は複数台であってもよい。 [First Embodiment]
<Configuration of air conditioner>
FIG. 1 is a configuration diagram of an air conditioner using a refrigeration apparatus according to the first embodiment of the present invention. In FIG. 1, the air conditioner 1 includes an outdoor unit 2 and an indoor unit 3. Note that a plurality of indoor units 3 may be provided.

この空調機１は、冷媒が充填された冷媒回路１０を備えている。冷媒には分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒が使用され、本実施形態では、Ｒ１２３４＋Ｒ３２が使用されている。冷媒回路１０は、室外ユニット２に収容された室外側回路と、室内ユニット３に収容された室内側回路とを備えている。室外側回路と室内側回路とは、ガス側連絡配管１７ａ及び液側連絡配管１７ｂによって接続されている。 The air conditioner 1 includes a refrigerant circuit 10 filled with a refrigerant. The refrigerant is composed of an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure. A non-azeotropic refrigerant mixture including a refrigerant is used, and R1234 + R32 is used in this embodiment. The refrigerant circuit 10 includes an outdoor circuit accommodated in the outdoor unit 2 and an indoor circuit accommodated in the indoor unit 3. The outdoor circuit and the indoor circuit are connected by a gas side communication pipe 17a and a liquid side communication pipe 17b.

＜室内ユニットの構成＞
室内側回路には、室内熱交換器４０が設けられている。室内熱交換器４０は、クロスフィン式のフィン・アンド・チューブ型熱交換器として構成されている。この室内熱交換器４０の近傍には、室内熱交換器４０に室内空気を送るための室内ファン２３が設けられている。 <Configuration of indoor unit>
An indoor heat exchanger 40 is provided in the indoor circuit. The indoor heat exchanger 40 is configured as a cross fin type fin-and-tube heat exchanger. An indoor fan 23 for sending indoor air to the indoor heat exchanger 40 is provided in the vicinity of the indoor heat exchanger 40.

＜室外ユニットの構成＞
室外ユニット２における室外側回路には、圧縮機２８、四路切換弁２９、室外熱交換器３０、及び膨張弁３４が接続されている。室外側回路の一端には、液側連絡配管１７ｂが接続される液側閉鎖弁１９が設けられている。室外側回路の他端には、ガス側連絡配管１７ａが接続されるガス側閉鎖弁１８が設けられている。圧縮機２８の吐出側は、四路切換弁２９の第１ポートＰ１に接続されている。圧縮機２８の吸入側は、四路切換弁２９の第３ポートＰ３に接続されている。 <Configuration of outdoor unit>
A compressor 28, a four-way switching valve 29, an outdoor heat exchanger 30, and an expansion valve 34 are connected to the outdoor circuit in the outdoor unit 2. At one end of the outdoor circuit, a liquid side closing valve 19 to which the liquid side communication pipe 17b is connected is provided. At the other end of the outdoor circuit, a gas side shut-off valve 18 to which a gas side communication pipe 17a is connected is provided. The discharge side of the compressor 28 is connected to the first port P1 of the four-way switching valve 29. The suction side of the compressor 28 is connected to the third port P3 of the four-way switching valve 29.

室外熱交換器３０は、補助熱交換器である第１熱交換器３１と、主熱交換器である第２熱交換器３２とから成り、第２熱交換器３２は、クロスフィン式のフィン・アンド・チューブ型熱交換器として構成されている。この第２熱交換器３２の近傍には、第２熱交換器３２及び第１熱交換器３１に室外空気を送るための室外ファン３３が設けられている。第２熱交換器３２の一端側は、四路切換弁２９の第４ポートＰ４に接続されている。第２熱交換器３２の他端側は、第１熱交換器３１の一端側に接続されている。   The outdoor heat exchanger 30 includes a first heat exchanger 31 that is an auxiliary heat exchanger and a second heat exchanger 32 that is a main heat exchanger, and the second heat exchanger 32 includes cross-fin fins. -It is configured as an and tube type heat exchanger. In the vicinity of the second heat exchanger 32, an outdoor fan 33 for sending outdoor air to the second heat exchanger 32 and the first heat exchanger 31 is provided. One end side of the second heat exchanger 32 is connected to the fourth port P4 of the four-way switching valve 29. The other end side of the second heat exchanger 32 is connected to one end side of the first heat exchanger 31.

第１熱交換器３１は、第２熱交換器３２と同様に、クロスフィン式のフィン・アンド・チューブ型熱交換器として構成されている。第１熱交換器３１の他端側は、減圧手段である膨張弁３４に接続されている。   Similar to the second heat exchanger 32, the first heat exchanger 31 is configured as a cross fin type fin-and-tube heat exchanger. The other end of the first heat exchanger 31 is connected to an expansion valve 34 that is a decompression unit.

膨張弁３４は、開度可変の電子膨張弁として構成されている。膨張弁３４は、液側閉鎖弁１９に接続されている。また、四路切換弁２９の第２ポートＰ２はガス側閉鎖弁１８に接続されている。   The expansion valve 34 is configured as an electronic expansion valve with a variable opening. The expansion valve 34 is connected to the liquid side closing valve 19. The second port P <b> 2 of the four-way switching valve 29 is connected to the gas side closing valve 18.

四路切換弁２９は、第１ポートＰ１と第２ポートＰ２が互いに連通して第３ポートＰ３と第４ポートＰ４が互いに連通する第１状態（図１に実線で示す状態）と、第１ポートＰ１と第４ポートＰ４が互いに連通して第２ポートＰ２と第３ポートＰ３が互いに連通する第２状態（図１に破線で示す状態）とが切り換え可能となっている。   The four-way switching valve 29 has a first state (state indicated by a solid line in FIG. 1) in which the first port P1 and the second port P2 communicate with each other and the third port P3 and the fourth port P4 communicate with each other, A second state (state indicated by a broken line in FIG. 1) in which the port P1 and the fourth port P4 communicate with each other and the second port P2 and the third port P3 communicate with each other can be switched.

図２は、室外ユニットの内部の平面図である。図２において、室外ユニット２は、仕切壁５１によって機械室５０ａと空気流通室５０ｂとに区画されたケーシング５０を備えている。機械室５０ａには、圧縮機２８、四路切換弁（図示省略）及び膨張弁（図示省略）が配置されている。また、空気流通室５０ｂには、第２熱交換器３２、第１熱交換器３１、及び室外ファン３３が配置されている。ケーシング５０では、空気流通室５０ｂの前面側に吸込口５６が形成され、空気流通室５０ｂの背面側に吹出口５７が形成されている。空気流通室５０ｂでは、室外ファン３３によって吸込口５６から吸い込まれた空気が吹出口５７へ向かって流通する。   FIG. 2 is a plan view of the inside of the outdoor unit. In FIG. 2, the outdoor unit 2 includes a casing 50 that is partitioned into a machine chamber 50 a and an air circulation chamber 50 b by a partition wall 51. A compressor 28, a four-way switching valve (not shown), and an expansion valve (not shown) are arranged in the machine room 50a. Moreover, the 2nd heat exchanger 32, the 1st heat exchanger 31, and the outdoor fan 33 are arrange | positioned at the air circulation chamber 50b. In the casing 50, the suction inlet 56 is formed in the front side of the air circulation chamber 50b, and the blower outlet 57 is formed in the back side of the air circulation chamber 50b. In the air circulation chamber 50 b, the air sucked from the suction port 56 by the outdoor fan 33 flows toward the blowout port 57.

図３は、第１実施形態に係る冷凍装置の室外熱交換器の斜視図である。図３において、第２熱交換器３２はパネル状に形成されている。第２熱交換器３２は、伝熱管１２と、伝熱管１２と接触する複数の第２フィン１１２とを有している。第２フィン１１２は、矩形の薄板であり、一定の間隔を隔てて平行に並べられ、上下方向に延びている。そして、第２フィン１１２には、Ｕ字状の伝熱管１２の直管部が貫通し、複数の冷媒流通路が形成されている。各冷媒流通路は、互いに並列に接続されている。各冷媒流通路のガス側の入口は、第２熱交換器３２のガス側に配置されたヘッダ（図示省略）に接続されている。各冷媒流通路の液側の入口は、第２熱交換器３２と第１熱交換器３１との間に配置された分流器５８を介して第１熱交換器３１に接続されている。第２熱交換器３２では、液側の入口が下側に設けられ、ガス側の入口が上側に設けられている。   FIG. 3 is a perspective view of the outdoor heat exchanger of the refrigeration apparatus according to the first embodiment. In FIG. 3, the second heat exchanger 32 is formed in a panel shape. The second heat exchanger 32 includes the heat transfer tube 12 and a plurality of second fins 112 that are in contact with the heat transfer tube 12. The second fins 112 are rectangular thin plates, are arranged in parallel at regular intervals, and extend in the vertical direction. The straight pipe portion of the U-shaped heat transfer tube 12 passes through the second fin 112, and a plurality of refrigerant flow passages are formed. The respective refrigerant flow passages are connected in parallel to each other. The gas-side inlet of each refrigerant flow passage is connected to a header (not shown) disposed on the gas side of the second heat exchanger 32. The liquid-side inlet of each refrigerant flow passage is connected to the first heat exchanger 31 via a flow divider 58 disposed between the second heat exchanger 32 and the first heat exchanger 31. In the second heat exchanger 32, the liquid side inlet is provided on the lower side, and the gas side inlet is provided on the upper side.

第１熱交換器３１は、細長いパネル状に形成されている。第１熱交換器３１は、第２熱交換器３２と同様に伝熱管１２と、伝熱管１２と接触する複数の第１フィン１１１とを有している。第１フィン１１１は、矩形の薄板であり、一定の間隔を隔てて平行に並べられ、上下方向に延びている。そして、第１フィン１１１には、Ｕ字状の伝熱管１２の直管部が貫通し、１つの冷媒流通路が形成されている。第１熱交換器３１では、第１フィン１１１の配列方向の一端側に伝熱管１２の両端が位置している。伝熱管１２の両端のうち一方は、分流器５８を介して第２熱交換器３２の各冷媒流通路に接続されている。伝熱管１２の両端のうち他方は、膨張弁（図示省略）に接続されている。   The first heat exchanger 31 is formed in an elongated panel shape. Similarly to the second heat exchanger 32, the first heat exchanger 31 includes the heat transfer tube 12 and a plurality of first fins 111 that are in contact with the heat transfer tube 12. The first fins 111 are rectangular thin plates, are arranged in parallel at regular intervals, and extend in the vertical direction. And the 1st fin 111 penetrates the straight pipe part of the U-shaped heat transfer tube 12, and forms one refrigerant flow passage. In the first heat exchanger 31, both ends of the heat transfer tube 12 are located on one end side in the arrangement direction of the first fins 111. One of both ends of the heat transfer tube 12 is connected to each refrigerant flow passage of the second heat exchanger 32 via a flow divider 58. The other of the two ends of the heat transfer tube 12 is connected to an expansion valve (not shown).

第１熱交換器３１は、高さが第２熱交換器３２に比べて低く、第２熱交換器３２の下側に重なるように設けられている。第１熱交換器３１には第２熱交換器３２を流れる冷媒よりも液成分が多く比重が大きい冷媒が流れるので、第１熱交換器３１を第２熱交換器３２の下側に重なるように配置することで、冷媒が流れやすくなる。   The first heat exchanger 31 is provided so as to be lower in height than the second heat exchanger 32 and overlap the lower side of the second heat exchanger 32. Since the refrigerant having more liquid components and higher specific gravity than the refrigerant flowing through the second heat exchanger 32 flows through the first heat exchanger 31, the first heat exchanger 31 overlaps the lower side of the second heat exchanger 32. It becomes easy to flow a refrigerant by arranging in.

第１熱交換器３１は、暖房運転時に蒸発器として働く室外熱交換器３０の冷媒入口側に位置する部分であり、着霜し易い。本実施形態では、第１フィン１１１の全表面に撥水性の被膜を形成する撥水性コーティングが施されており、着霜し難くなっている。   The 1st heat exchanger 31 is a part located in the refrigerant | coolant inlet side of the outdoor heat exchanger 30 which functions as an evaporator at the time of heating operation, and it is easy to form frost. In the present embodiment, a water-repellent coating that forms a water-repellent film is applied to the entire surface of the first fin 111, and frost formation is difficult.

撥水性コーティングには、撥水性のバインダー樹脂、ＰＴＦＥ（ポリテトラフルオロエチレン）粒子、及び分散剤からなる表面処理用組成物が用いられている。この表面処理用組成物は、さらに低熱容量の粒子や、溶媒を含んでいてもよい。撥水性のバインダー樹脂としては、例えば、ダイキン工業（株）製のゼッフルＧＫ−５１０などが採用される。   For the water-repellent coating, a surface treatment composition comprising a water-repellent binder resin, PTFE (polytetrafluoroethylene) particles, and a dispersant is used. This surface treatment composition may further contain particles having a low heat capacity and a solvent. As the water repellent binder resin, for example, Zaffle GK-510 manufactured by Daikin Industries, Ltd. is used.

ＰＴＦＥ粒子としては、例えば、セントラル硝子（株）製のセフラルルーブ（平均粒子径５〜１０μｍの変性ＰＴＦＥ、重量平均分子量１５００〜２００００）が採用される。また、分散剤としては、例えば、ダイキン工業（株）製のユニダインＴＧ−６５６が採用される。   As PTFE particles, for example, Cephalal Lube (modified PTFE having an average particle diameter of 5 to 10 μm, weight average molecular weight of 1500 to 20000) manufactured by Central Glass Co., Ltd. is employed. As the dispersant, for example, Unidyne TG-656 manufactured by Daikin Industries, Ltd. is employed.

また、任意成分である低熱容量の粒子としては、例えば、カーボンブラック粒子や結晶性カーボンブラック粒子が採用される。また、任意成分である溶媒としては、例えば、酢酸ブチルが採用される。   Moreover, as the low heat capacity particles which are optional components, for example, carbon black particles and crystalline carbon black particles are employed. Moreover, as a solvent which is an arbitrary component, butyl acetate is employ | adopted, for example.

塗膜の強度を高めるために、例えば、バインダー樹脂として化学的硬化性反応性基を有する樹脂を使用し、かつ架橋剤としてイソシアネート化合物を用いる。   In order to increase the strength of the coating film, for example, a resin having a chemically curable reactive group is used as a binder resin, and an isocyanate compound is used as a crosslinking agent.

また、硬化促進剤を使用する場合は、例えば、有機スズ化合物、酸性リン酸エステル、酸性リン酸エステルとアミン化合物との反応生成物、アミン系化合物、オクチル酸鉛などから単独又は２種以上併用したものが使用される。   In addition, when using a curing accelerator, for example, an organic tin compound, an acidic phosphate ester, a reaction product of an acidic phosphate ester with an amine compound, an amine compound, lead octylate or the like alone or in combination of two or more kinds Used.

被膜の形成にあたっては、例えばディップコート法、バーコート法、ロールコート法、スプレー法などの方法によって、第１フィン１１１の表面を塗装する。そして、塗布後、室温で乾燥するか、必要に応じて加熱乾燥させて被膜を形成する。この被膜上では、水滴の水接触角が１５０度程度になる。また、コーティング面を傾けた場合に水滴が滑り始める滑落角が、４μＬの水滴で１０から１５度程度になり、１０μＬの水滴で１０度以下になる。   In forming the coating, the surface of the first fin 111 is applied by a method such as a dip coating method, a bar coating method, a roll coating method, or a spray method. And after application | coating, it dries at room temperature or heat-drys as needed, and forms a film. On this film, the water contact angle of the water droplet is about 150 degrees. Further, the sliding angle at which the water droplet starts to slide when the coating surface is tilted is about 10 to 15 degrees with a 4 μL water droplet, and becomes 10 degrees or less with a 10 μL water droplet.

なお、本実施形態では、第１熱交換器３１がさらに着霜し難くなるように、第１フィン１１１は第２熱交換器３２の第２フィン１１２よりも間隔が広く設定されており、第２フィン１１２よりも第１フィン１１１の通風抵抗が低くなっている。   In the present embodiment, the first fins 111 are set wider than the second fins 112 of the second heat exchanger 32 so that the first heat exchanger 31 is more difficult to form frost. The ventilation resistance of the first fin 111 is lower than that of the two fins 112.

＜空調機の動作＞
空調機１では、四路切換弁２９によって冷房運転と暖房運転と除霜運転とが切り換えが行われる。 <Operation of air conditioner>
In the air conditioner 1, the cooling operation, the heating operation, and the defrosting operation are switched by the four-way switching valve 29.

（暖房運転）
暖房運転では、四路切換弁２９が第１状態（実線）に設定される。そして、この状態で圧縮機２８を運転すると、冷媒回路１０では、第１熱交換器３１及び第２熱交換器３２が蒸発器となって、室内熱交換器４０が凝縮器となる蒸気圧縮冷凍サイクルが行われる。暖房運転では、第１熱交換器３１が蒸発器の入口側部分になる。 (Heating operation)
In the heating operation, the four-way switching valve 29 is set to the first state (solid line). When the compressor 28 is operated in this state, in the refrigerant circuit 10, the first heat exchanger 31 and the second heat exchanger 32 serve as an evaporator and the indoor heat exchanger 40 serves as a condenser. A cycle is performed. In the heating operation, the first heat exchanger 31 is an inlet side portion of the evaporator.

圧縮機２８から吐出された高圧の冷媒は、室内熱交換器４０で室内空気と熱交換して凝縮する。凝縮した冷媒は、膨張弁３４を通過する際に減圧された後、第１熱交換器３１及び第２熱交換器３２で室外空気と熱交換して蒸発する。第２熱交換器３２を通過した冷媒は、圧縮機２８へ吸入されて圧縮される。   The high-pressure refrigerant discharged from the compressor 28 is condensed by exchanging heat with indoor air in the indoor heat exchanger 40. The condensed refrigerant is decompressed when passing through the expansion valve 34, and then evaporates by exchanging heat with outdoor air in the first heat exchanger 31 and the second heat exchanger 32. The refrigerant that has passed through the second heat exchanger 32 is sucked into the compressor 28 and compressed.

暖房運転時、第１熱交換器３１及び第２熱交換器３２に接触した空気中の水分は、凝縮して第１熱交換器３１及び第２熱交換器３２の第１フィン１１１及び第２フィン１１２の表面に付着する。第１熱交換器３１の第１フィン１１１には撥水性コーティングが施されているので、第１熱交換器３１の第１フィン１１１に付着した水分は、第１フィン１１１の間を通過する空気によって流されたり、重力によって下方へ落下したりする。その結果、第１熱交換器３１において冷媒の蒸発温度が０℃以下になる部分があっても、第１熱交換器３１の表面に付着した水滴の多くは凝固する前に第１熱交換器３１の表面から取り除かれるので、第１熱交換器３１の表面の着霜量を減少させることができる。   During the heating operation, moisture in the air that has contacted the first heat exchanger 31 and the second heat exchanger 32 is condensed and the first fins 111 and the second fins of the first heat exchanger 31 and the second heat exchanger 32 are condensed. It adheres to the surface of the fin 112. Since the first fin 111 of the first heat exchanger 31 is provided with a water-repellent coating, moisture adhering to the first fin 111 of the first heat exchanger 31 is air passing between the first fins 111. Or fall down due to gravity. As a result, even if there is a portion in the first heat exchanger 31 where the evaporation temperature of the refrigerant is 0 ° C. or less, most of the water droplets adhering to the surface of the first heat exchanger 31 are solidified before being solidified. Since it is removed from the surface of 31, the amount of frost formation on the surface of the first heat exchanger 31 can be reduced.

また、第２熱交換器３２では、第１熱交換器３１に比べて冷媒の蒸発温度が高くなるので、第２熱交換器３２の表面に付着した水滴は凝固しにくく、第２熱交換器３２では着霜が生じにくい。   Moreover, in the 2nd heat exchanger 32, since the evaporation temperature of a refrigerant | coolant becomes high compared with the 1st heat exchanger 31, the water droplet adhering to the surface of the 2nd heat exchanger 32 cannot be solidified easily, and the 2nd heat exchanger In 32, frost formation hardly occurs.

また、第２熱交換器３２のうち第１熱交換器３１と重なる部分では、通過する空気中の水分が、第１熱交換器３１を通過する際に凝縮してある程度取り除かれている。その結果、上記重なる部分では、凝縮する水分量が少なくなるので、着霜量が低減される。   Moreover, in the part which overlaps with the 1st heat exchanger 31 among the 2nd heat exchangers 32, the water | moisture content in the passing air is condensed and removed when passing the 1st heat exchanger 31 to some extent. As a result, the amount of moisture to be condensed is reduced in the overlapping portion, so that the amount of frost formation is reduced.

（冷房運転）
冷房運転では、四路切換弁２９が第２状態（点線）に設定される。この状態で圧縮機２８を運転すると、冷媒回路１０では第２熱交換器３２及び第１熱交換器３１が凝縮器となって室内熱交換器４０が蒸発器となる蒸気圧縮冷凍サイクルが行われる。 (Cooling operation)
In the cooling operation, the four-way switching valve 29 is set to the second state (dotted line). When the compressor 28 is operated in this state, the refrigerant circuit 10 performs a vapor compression refrigeration cycle in which the second heat exchanger 32 and the first heat exchanger 31 serve as a condenser and the indoor heat exchanger 40 serves as an evaporator. .

圧縮機２８から吐出された高圧の冷媒は、第２熱交換器３２で室外空気と熱交換して凝縮する。第１熱交換器３１では、第２熱交換器３２で凝縮しきれていない冷媒が凝縮すると共に、冷媒がさらに冷却されて過冷却状態になる。   The high-pressure refrigerant discharged from the compressor 28 is condensed by exchanging heat with outdoor air in the second heat exchanger 32. In the 1st heat exchanger 31, while the refrigerant | coolant which has not been condensed by the 2nd heat exchanger 32 condenses, a refrigerant | coolant is further cooled and it will be in a supercooled state.

第１熱交換器３１を通過した冷媒は、膨張弁３４を通過する際に減圧され、その後に室内熱交換器４０で室内空気と熱交換して蒸発する。室内熱交換器４０を通過した冷媒は、圧縮機２８へ吸入されて圧縮される。   The refrigerant that has passed through the first heat exchanger 31 is depressurized when passing through the expansion valve 34, and then evaporates by exchanging heat with indoor air in the indoor heat exchanger 40. The refrigerant that has passed through the indoor heat exchanger 40 is sucked into the compressor 28 and compressed.

（除霜運転）
除霜運転は、暖房運転中に必要に応じて行なわれる。空調機１では、第１熱交換器３１に撥水性コーティングが施されているので、暖房運転時に着霜が生じにくくなっているが、運転条件によっては例えば第２熱交換器３２の着霜量が多くなって除霜運転が必要になる場合がある。例えば、第２熱交換器３２の温度センサなどから除霜運転が必要であると判断されると除霜運転が実行される。 (Defrosting operation)
The defrosting operation is performed as necessary during the heating operation. In the air conditioner 1, since the water repellent coating is applied to the first heat exchanger 31, frost formation is less likely to occur during heating operation, but depending on the operation conditions, for example, the frost formation amount of the second heat exchanger 32 May increase and defrosting operation may be required. For example, when it is determined from the temperature sensor of the second heat exchanger 32 that the defrosting operation is necessary, the defrosting operation is executed.

除霜運転では、圧縮機２８が停止されて室外ファン３３のみが運転される。第２熱交換器３２には、低温の冷媒が流入しない状態で室外空気が送り込まれる。第２熱交換器３２に付着した氷は、室外空気によって暖められて融解される。   In the defrosting operation, the compressor 28 is stopped and only the outdoor fan 33 is operated. Outdoor air is fed into the second heat exchanger 32 in a state in which a low-temperature refrigerant does not flow. The ice adhering to the second heat exchanger 32 is heated and melted by the outdoor air.

コーティングには、撥水性を有するシリコ−ン系の塗料を用いてもよいし、撥水性を有するフッ素樹脂系の塗料を用いてもよい。また、フッ素系高分子とシリコン系樹脂をグラウトさせ、かつ親水性原子団を結合させてナノ相分離構造を形成させた、滑水性を有するコーティング材料を用いてもよい。このコーティングによる被膜上では、２０μＬの水滴の場合の滑落角が１５度から２０度程度の値になる。   For the coating, a water-repellent silicone-based paint may be used, or a water-repellent fluororesin-based paint may be used. Alternatively, a coating material having water slidability in which a fluoropolymer and a silicon resin are grouted and a hydrophilic atomic group is bonded to form a nanophase separation structure may be used. On the film formed by this coating, the sliding angle in the case of a 20 μL water droplet is about 15 to 20 degrees.

また、着霜防止処理として、撥水性、又は滑水性の被膜を形成する処理に限定されるものではなく、着霜防止処理として、親水性の被膜を形成する処理を施してもよい。親水性の被膜上では、結露水は広がり易くなる反面、降下する速度が早くなる。その結果、結露水が素早く落下するので、氷結する水滴が減少し着霜量も減少する。   Further, the frosting prevention process is not limited to the process of forming a water-repellent or water-slidable film, and a process of forming a hydrophilic film may be performed as the frosting prevention process. On the hydrophilic film, the condensed water tends to spread, but the rate of descending is faster. As a result, the condensed water quickly drops, so that water droplets that freeze are reduced and the amount of frost formation is also reduced.

＜第１実施形態の第１変形例＞
図４は、第１変形例に係る冷凍装置の室外熱交換器の斜視図である。図４において、室外熱交換器３０は、１つの熱交換器が上下に分割された構成であり、吸込口側となる下側部分が第１熱交換器３１であり、上側部分が第２熱交換器３２である。第１熱交換器３１の第１フィン１１１は、第２熱交換器３２の第２フィン１１２よりも間隔が広く設定され、且つ上記実施形態と同じ撥水性コーティングが施されている。第１熱交換器３１は伝熱管１２によって２つの冷媒流通路が形成され、第２熱交換器３２は伝熱管１２によって４つの冷媒流通路が形成されている。第１熱交換器３１の２つの冷媒流通路と、第２熱交換器３２の４つの冷媒流通路との間には、分流器５８が設けられている。 <First Modification of First Embodiment>
FIG. 4 is a perspective view of an outdoor heat exchanger of the refrigeration apparatus according to the first modification. In FIG. 4, the outdoor heat exchanger 30 has a configuration in which one heat exchanger is divided into upper and lower parts, the lower part on the suction port side is the first heat exchanger 31, and the upper part is the second heat. This is the exchanger 32. The first fins 111 of the first heat exchanger 31 are set wider than the second fins 112 of the second heat exchanger 32, and are provided with the same water-repellent coating as in the above embodiment. In the first heat exchanger 31, two refrigerant flow paths are formed by the heat transfer tubes 12, and in the second heat exchanger 32, four refrigerant flow paths are formed by the heat transfer tubes 12. A flow divider 58 is provided between the two refrigerant flow passages of the first heat exchanger 31 and the four refrigerant flow passages of the second heat exchanger 32.

暖房運転時、室外熱交換器３０の第１熱交換器３１の冷媒流通路から冷媒が流通し、分流器５８で分岐して、第２熱交換器３２の各冷媒流通路を流通する。つまり、第１熱交換器３１は、液側部分であって暖房運転時の室外熱交換器３０の冷媒入口側に位置する部分に相当する。   During the heating operation, the refrigerant flows from the refrigerant flow passage of the first heat exchanger 31 of the outdoor heat exchanger 30, branches by the flow divider 58, and flows through the refrigerant flow passages of the second heat exchanger 32. That is, the first heat exchanger 31 corresponds to a liquid side portion and a portion located on the refrigerant inlet side of the outdoor heat exchanger 30 during the heating operation.

＜第１実施形態の第２変形例＞
図５は、第２変形例に係る冷凍装置の室外熱交換器の斜視図である。図５において、室外熱交換器３０は、フィン１１のうち吸込口側の下側部分に、上記実施形態と同じ撥水性コーティングが施されている。撥水性コーティングによる被膜が形成されている部分を貫通する伝熱管によって２つの冷媒流通路が形成され、被膜がない部分を貫通する伝熱管によって４つの冷媒流通路が形成されている。被膜が形成されている部分の冷媒流通路と、被膜がない部分の４つの冷媒流通路との間には、分流器５８が設けられている。 <Second Modification of First Embodiment>
FIG. 5 is a perspective view of an outdoor heat exchanger of the refrigeration apparatus according to the second modification. In FIG. 5, the outdoor heat exchanger 30 is provided with the same water-repellent coating as that of the above embodiment on the lower portion of the fin 11 on the suction port side. Two refrigerant flow passages are formed by the heat transfer tubes that pass through the portion where the film is formed by the water repellent coating, and four refrigerant flow passages are formed by the heat transfer tubes that pass through the portion where there is no coating. A flow divider 58 is provided between the refrigerant flow passage where the coating is formed and the four refrigerant flow passages where there is no coating.

暖房運転時、室外熱交換器３０のうち被膜が形成されている部分の冷媒流通路から冷媒が流通し、分流器５８で分岐して、被膜がない部分の各冷媒流通路を流通する。つまり、被膜が形成されている部分は、液側部分であって暖房運転時の室外熱交換器３０の冷媒入口側に位置する部分に相当する。   During the heating operation, the refrigerant flows from the refrigerant flow passage in the portion of the outdoor heat exchanger 30 where the coating is formed, branches by the flow divider 58, and flows through the respective refrigerant flow passages in the portion without the coating. That is, the part in which the film is formed corresponds to a liquid side part and a part located on the refrigerant inlet side of the outdoor heat exchanger 30 during the heating operation.

＜第１実施形態の特徴＞
（１）
この冷凍装置は、非共沸混合冷媒（Ｒ１２３４＋Ｒ３２）使用する冷凍装置であり、暖房運転時に蒸発器となる室外熱交換器３０を備えている。室外熱交換器３０は、第１熱交換器３１と第２熱交換器３２とを有し、第１熱交換器３１が冷媒の入口側に位置している。第１熱交換器３１の第１フィン１１１のみに撥水性の被膜を形成する着霜防止処理が施されている。第１熱交換器３１は、最も温度が低く着霜し易い部分であるが、着霜し易い部分に着霜防止処理が施されているので着霜し難くなる。また、第１熱交換器３１の第１フィン１１１と、第２熱交換器３２の第２フィン１１２とは分割されているので、室外熱交換器３０全体に着霜防止処理を施したものと比較して、製造コストが低い。 <Features of First Embodiment>
(1)
This refrigeration apparatus is a refrigeration apparatus that uses a non-azeotropic refrigerant mixture (R1234 + R32), and includes an outdoor heat exchanger 30 that serves as an evaporator during heating operation. The outdoor heat exchanger 30 includes a first heat exchanger 31 and a second heat exchanger 32, and the first heat exchanger 31 is located on the refrigerant inlet side. The frosting prevention process which forms a water-repellent film only on the 1st fin 111 of the 1st heat exchanger 31 is performed. Although the 1st heat exchanger 31 is the part where temperature is the lowest and it is easy to form frost, since the frost formation prevention process is performed to the part which is easy to form frost, it becomes difficult to form frost. Moreover, since the 1st fin 111 of the 1st heat exchanger 31 and the 2nd fin 112 of the 2nd heat exchanger 32 are divided | segmented, what performed the frost formation prevention process to the outdoor heat exchanger 30 whole. In comparison, the manufacturing cost is low.

（２）
この冷凍装置では、第１熱交換器３１の第１フィン１１１の間隔が、第２熱交換器３２の第２フィン１１２の間隔よりも大きく、第１フィン１１１のフィン形状が、伝熱管１２との接触部を除いて切り起しのない平板状である。その結果、着霜し難くなり運転時間が長く維持され、暖房運転効率が向上する。 (2)
In this refrigeration apparatus, the interval between the first fins 111 of the first heat exchanger 31 is larger than the interval between the second fins 112 of the second heat exchanger 32, and the fin shape of the first fins 111 is different from that of the heat transfer tube 12. It is a flat plate shape without cutting up except for the contact portion. As a result, frost formation becomes difficult and the operation time is maintained for a long time, and the heating operation efficiency is improved.

〔第２実施形態〕
第１実施形態、第１変形例及び第２変形例では、暖房運転時に蒸発器となる室外熱交換器３０が着霜することを前提にして、室外熱交換器３０の一部に撥水性コーティングを施しているが、冷房運転時に蒸発器となる室内熱交換器４０の一部に撥水性コーティングを施してもよい。 [Second Embodiment]
In the first embodiment, the first modified example, and the second modified example, a water repellent coating is applied to a part of the outdoor heat exchanger 30 on the assumption that the outdoor heat exchanger 30 serving as an evaporator is frosted during heating operation. However, a water-repellent coating may be applied to a part of the indoor heat exchanger 40 that serves as an evaporator during the cooling operation.

図６は、本発明の第２実施形態に係る冷凍装置を用いた空調機の構成図である。図６において、室内熱交換器４０は、補助熱交換器４１と、主熱交換器４２とを有している。補助熱交換器４１と主熱交換器４２との間には、第２膨張弁４３が接続されている。   FIG. 6 is a configuration diagram of an air conditioner using the refrigeration apparatus according to the second embodiment of the present invention. In FIG. 6, the indoor heat exchanger 40 includes an auxiliary heat exchanger 41 and a main heat exchanger 42. A second expansion valve 43 is connected between the auxiliary heat exchanger 41 and the main heat exchanger 42.

除湿運転では、四路切換弁２９が第２状態（点線）に設定される。このとき、膨張弁３４は全開である。第２膨張弁４３は、補助熱交換器４１と主熱交換器４２との間の冷媒流路を絞り、室外熱交換器３０と補助熱交換器４１とを凝縮器として機能させ、主熱交換器４２を蒸発器として機能させる。その結果、室内温度を下げずに除湿運転を行うことができる。   In the dehumidifying operation, the four-way switching valve 29 is set to the second state (dotted line). At this time, the expansion valve 34 is fully open. The second expansion valve 43 restricts the refrigerant flow path between the auxiliary heat exchanger 41 and the main heat exchanger 42, causes the outdoor heat exchanger 30 and the auxiliary heat exchanger 41 to function as a condenser, and performs main heat exchange. The vessel 42 functions as an evaporator. As a result, the dehumidifying operation can be performed without lowering the room temperature.

図７は、第２実施形態に係る冷凍装置の室内熱交換器の斜視図である。図７において、主熱交換器４２は、第１熱交換部４２ａ及び第２熱交換部４２ｂの２つに分割され、第１熱交換部４２ａと第２熱交換部４２ｂとによって逆Ｖ字形を形成している。   FIG. 7 is a perspective view of the indoor heat exchanger of the refrigeration apparatus according to the second embodiment. In FIG. 7, the main heat exchanger 42 is divided into two parts, a first heat exchange part 42a and a second heat exchange part 42b, and an inverted V-shape is formed by the first heat exchange part 42a and the second heat exchange part 42b. Forming.

補助熱交換器４１は、第１補助熱交換部４１ａ及び第２補助熱交換部４１ｂに分割されている。第１補助熱交換部４１ａは第１熱交換部４２ａの風上側に配置され、第２補助熱交換部４１ｂは第２熱交換部４２ｂの風上側に配置されている。   The auxiliary heat exchanger 41 is divided into a first auxiliary heat exchange unit 41a and a second auxiliary heat exchange unit 41b. The first auxiliary heat exchange part 41a is arranged on the windward side of the first heat exchange part 42a, and the second auxiliary heat exchange part 41b is arranged on the windward side of the second heat exchange part 42b.

補助熱交換器４１は、冷房運転時に室内熱交換器４０の冷媒入口側に位置する部分であるので、第１フィン１１１の全表面に撥水性の被膜を形成する撥水性コーティングが施され、着霜を防止している。   Since the auxiliary heat exchanger 41 is a portion located on the refrigerant inlet side of the indoor heat exchanger 40 during the cooling operation, a water repellent coating that forms a water repellent film is applied to the entire surface of the first fin 111, Prevents frost.

冷房運転時、主熱交換器４２及び補助熱交換器４１は、共に蒸発器として機能する。主熱交換器４２及び補助熱交換器４１に接触した空気中の水分は、凝縮して補助熱交換器４１及び主熱交換器４２の第１フィン１１１及び第２フィン１１２の表面に付着する。補助熱交換器４１の第１フィンには撥水性コーティングが施されているので、補助熱交換器４１の第１フィン１１１に付着した水分は、第１フィン１１１の間を通過する空気によって流されたり、重力によって下方へ落下したりする。その結果、補助熱交換器４１において冷媒の蒸発温度が０℃以下になる部分があっても、補助熱交換器４１の表面に付着した水滴の多くは凝固する前に補助熱交換器４１の表面から取り除かれるので、補助熱交換器４１の表面の着霜量を減少させることができる。   During the cooling operation, both the main heat exchanger 42 and the auxiliary heat exchanger 41 function as an evaporator. Moisture in the air that has contacted the main heat exchanger 42 and the auxiliary heat exchanger 41 is condensed and adheres to the surfaces of the first fins 111 and the second fins 112 of the auxiliary heat exchanger 41 and the main heat exchanger 42. Since the first fin of the auxiliary heat exchanger 41 is provided with a water-repellent coating, moisture adhering to the first fin 111 of the auxiliary heat exchanger 41 is caused to flow by the air passing between the first fins 111. Or fall downward due to gravity. As a result, even if there is a part in the auxiliary heat exchanger 41 where the evaporation temperature of the refrigerant is 0 ° C. or less, most of the water droplets adhering to the surface of the auxiliary heat exchanger 41 are solidified before they are solidified. Therefore, the amount of frost formation on the surface of the auxiliary heat exchanger 41 can be reduced.

なお、第２実施形態では、補助熱交換器４１がさらに着霜し難くなるように、第１フィン１１１は主熱交換器４２の第２フィン１１２よりも間隔が広く設定されており、第２フィン１１２よりも第１フィン１１１の通風抵抗が低くなっている。   In the second embodiment, the first fins 111 are set wider than the second fins 112 of the main heat exchanger 42 so that the auxiliary heat exchanger 41 is more difficult to form frost. The ventilation resistance of the first fin 111 is lower than that of the fin 112.

また、主熱交換器４２では、補助熱交換器４１に比べて冷媒の蒸発温度が高くなるので、主熱交換器４２の表面に付着した水滴は凝固しにくく、主熱交換器４２では着霜が生じにくい。   Further, since the refrigerant evaporating temperature is higher in the main heat exchanger 42 than in the auxiliary heat exchanger 41, water droplets adhering to the surface of the main heat exchanger 42 are difficult to solidify, and the main heat exchanger 42 is frosted. Is unlikely to occur.

また、主熱交換器４２のうち補助熱交換器４１と重なる部分では、通過する空気中の水分が、補助熱交換器４１を通過する際に凝縮してある程度取り除かれている。その結果、上記重なる部分では、凝縮する水分量が少なくなるので、着霜量が低減される。   Moreover, in the part which overlaps with the auxiliary heat exchanger 41 among the main heat exchangers 42, the moisture in the passing air is condensed and removed to some extent when passing through the auxiliary heat exchanger 41. As a result, the amount of moisture to be condensed is reduced in the overlapping portion, so that the amount of frost formation is reduced.

＜第２実施形態の特徴＞
この冷凍装置は、非共沸混合冷媒（Ｒ１２３４＋Ｒ３２）使用する冷凍装置であり、冷房運転時に蒸発器となる室内熱交換器４０を備えている。室内熱交換器４０は、補助熱交換器４１と主熱交換器４２とを有し、補助熱交換器４１が冷媒の入口側に位置している。そして、補助熱交換器４１の第１フィン１１１のみに撥水性の被膜を形成する着霜防止処理が施されている。補助熱交換器４１は、最も温度が低く着霜し易い部分であるが、着霜し易い部分に着霜防止処理が施されているので着霜し難くなる。また、補助熱交換器４１の第１フィン１１１と、主熱交換器４２の第２フィン１１２とは分割されているので、室外熱交換器３０全体に着霜防止処理を施したものと比較して、製造コストが低い。 <Features of Second Embodiment>
This refrigeration apparatus is a refrigeration apparatus that uses a non-azeotropic refrigerant mixture (R1234 + R32), and includes an indoor heat exchanger 40 that serves as an evaporator during cooling operation. The indoor heat exchanger 40 includes an auxiliary heat exchanger 41 and a main heat exchanger 42, and the auxiliary heat exchanger 41 is located on the refrigerant inlet side. And the anti-frosting process which forms a water-repellent film only in the 1st fin 111 of the auxiliary heat exchanger 41 is performed. The auxiliary heat exchanger 41 has the lowest temperature and is likely to be frosted. However, the frosting prevention process is performed on the portion that is likely to be frosted, so that it is difficult to frost. Moreover, since the 1st fin 111 of the auxiliary heat exchanger 41 and the 2nd fin 112 of the main heat exchanger 42 are divided | segmented, compared with what performed the frost formation prevention process to the outdoor heat exchanger 30 whole. The manufacturing cost is low.

＜その他の実施形態＞
第１実施形態、第１変形例、第２変形例及び第２実施形態では、冷媒として、ＨＦＯ−１２３４ｙｆとＨＦＣ−３２の２種類の有機化合物からなる混合冷媒を使用しているが、ＨＦＣ−３２の割合は、２２質量％のＨＦＣ−３２との混合冷媒である。ＨＦＣ−３２の割合は、６質量％以上３０質量％以下であればよく、好ましくは、１３質量％以上２３質量％以下であればよく、更に好ましくは、２１質量％以上２３質量％以下であればよい。 <Other embodiments>
In the first embodiment, the first modified example, the second modified example, and the second embodiment, a mixed refrigerant composed of two types of organic compounds, HFO-1234yf and HFC-32, is used as the refrigerant. The ratio of 32 is a mixed refrigerant with 22% by mass of HFC-32. The ratio of HFC-32 may be 6% by mass or more and 30% by mass or less, preferably 13% by mass or more and 23% by mass or less, and more preferably 21% by mass or more and 23% by mass or less. That's fine.

また、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒と、１０質量％以上のＨＦＣ−１２５（ペンタフルオロエタン、ＣＦ3−ＣＨＦ2）との混合冷媒でもよい。ＨＦＣ−１２５の割合は、１０質量％以上２０質量％以下であれば好ましい。 A refrigerant composed of an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure. And 10% by mass or more of HFC-125 (pentafluoroethane, CF 3 —CHF 2 ). The ratio of HFC-125 is preferably 10% by mass or more and 20% by mass or less.

また、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒と、ＨＦＣ−１３４（１，１，２，２−テトラフルオロエタン、ＣＨＦ2−ＣＨＦ2）、ＨＦＣ−１３４ａ（１，１，１，２−テトラフルオロエタン、ＣＨ2Ｆ−ＣＦ3）、ＨＦＣ−１４３ａ（１，１，１−トリフルオロエタン、ＣＨ3ＣＦ3）、ＨＦＣ−１５２ａ（１，１−ジフルオロエタン、ＣＨＦ2−ＣＨ3）、ＨＦＣ−１６１（フルオロエタン、ＣＨ3−ＣＨ2Ｆ）、ＨＦＣ−２２７ｅａ（１，１，１，２，３，３，３−ヘプタフルオロプロパン、ＣＦ3−ＣＨＦ−ＣＦ3）、ＨＦＣ−２３６ｅａ（１，１，１，２，３，３−ヘキサフルオロプロパン、ＣＦ3−ＣＨＦ−ＣＨＦ2）、ＨＦＣ−２３６ｆａ（１，１，１，３，３，３−ヘキサフルオロエタン、ＣＦ3−ＣＨ2−ＣＦ3）、及びＨＦＣ−３６５ｍｆｃ（１，１，１，３，３−ペンタフルオロブタン、ＣＦ3−ＣＨ2ＣＦ2−ＣＨ3）のいずれか１つとの混合冷媒でもよい。 A refrigerant composed of an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure. HFC-134 (1,1,2,2-tetrafluoroethane, CHF 2 -CHF 2 ), HFC-134a (1,1,1,2-tetrafluoroethane, CH 2 F-CF 3 ), HFC -143a (1,1,1- trifluoroethane, CH 3 CF 3), HFC -152a (1,1- difluoroethane, CHF 2 -CH 3), HFC -161 ( fluoroethane, CH 3 -CH 2 F) , HFC-227ea (1,1,1,2,3,3,3-heptafluoropropane, CF 3 —CHF—CF 3 ), HFC-236ea (1,1,1,2,3,3-hexafluoro propane, CF 3 -CHF-CHF 2 ), HFC-236fa (1,1,1,3,3,3-hexafluoroethane, CF 3 —CH 2 —CF 3 ), and HFC-365mfc (1,1,1,3,3-pentafluoro A mixed refrigerant with any one of butane and CF 3 —CH 2 CF 2 —CH 3 ) may be used.

また、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒と、炭化水素系冷媒との混合冷媒であってもよい。 The molecular formula C 3 H m F n (where, m = 1~5, n = 1~5 , and m + n = 6) refrigerant comprising an organic compound having one double bond and molecular structure represented by And a mixed refrigerant with a hydrocarbon-based refrigerant.

具体的には、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒と、メタン（ＣＨ4）、エタン（ＣＨ3−ＣＨ3）、プロパン（ＣＨ3−ＣＨ2−ＣＨ3）、プロペン（ＣＨ3−ＣＨ＝ＣＨ2）、ブタン（ＣＨ3−ＣＨ2−ＣＨ2−ＣＨ3）、イソブタン（ＣＨ3−ＣＨ（ＣＨ3）−ＣＨ3）、ペンタン（ＣＨ3−ＣＨ2−ＣＨ2−ＣＨ2−ＣＨ3）、２−メチルブタン（ＣＨ3−ＣＨ（ＣＨ3）−ＣＨ2−ＣＨ3）、及びシクロペンタン（ｃｙｃｌｏ−Ｃ5Ｈ10）のいずれか１つとの混合冷媒でもよい。 Specifically, an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure A refrigerant comprising methane (CH 4 ), ethane (CH 3 —CH 3 ), propane (CH 3 —CH 2 —CH 3 ), propene (CH 3 —CH═CH 2 ), butane (CH 3 —CH 2). -CH 2 -CH 3), isobutane (CH 3 -CH (CH 3) -CH 3), pentane (CH 3 -CH 2 -CH 2 -CH 2 -CH 3), 2- methylbutane (CH 3 -CH ( It may be a mixed refrigerant with any one of CH 3 ) —CH 2 —CH 3 ) and cyclopentane (cyclo-C 5 H 10 ).

また、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒と、ジメチルエーテル（ＣＨ3−Ｏ−ＣＨ3）、ビス−トリフルオロメチル−サルファイド（ＣＦ3−Ｓ−ＣＦ3）、二酸化炭素（ＣＯ2）、及びヘリウム（Ｈｅ）のいずれか１つとの混合冷媒でもよい。 A refrigerant composed of an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure. And a mixed refrigerant of dimethyl ether (CH 3 —O—CH 3 ), bis-trifluoromethyl-sulfide (CF 3 —S—CF 3 ), carbon dioxide (CO 2 ), and helium (He) But you can.

また、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒と、上記第２成分のいずれか２つとから成る混合冷媒を使用してもよい。例えば、５２質量％のＨＦＯ−１２３４ｙｆと、２３質量％のＨＦＣ−３２と、２５質量％のＨＦＣ−１２５から成る混合冷媒が好ましい。 A refrigerant composed of an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure. And a mixed refrigerant composed of any two of the second components may be used. For example, a mixed refrigerant composed of 52% by mass of HFO-1234yf, 23% by mass of HFC-32, and 25% by mass of HFC-125 is preferable.

以上のように、本発明によれば、分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を使用する冷凍装置を備えた空調機に有用である。 As described above, according to the present invention, the molecular formula is C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6), and a double bond is present in the molecular structure. It is useful for an air conditioner equipped with a refrigeration apparatus that uses a non-azeotropic refrigerant mixture including a refrigerant composed of an organic compound having one of the above.

本発明に第１実施形態に係る冷凍装置を用いた空調機の構成図。The block diagram of the air conditioner using the freezing apparatus which concerns on 1st Embodiment in this invention. 室外ユニットの内部の平面図。The top view inside an outdoor unit. 第１実施形態に係る冷凍装置の室外熱交換器の斜視図The perspective view of the outdoor heat exchanger of the freezing apparatus which concerns on 1st Embodiment. 第１変形例に係る冷凍装置の室外熱交換器の斜視図。The perspective view of the outdoor heat exchanger of the freezing apparatus which concerns on a 1st modification. 第２変形例に係る冷凍装置の室外熱交換器の斜視図。The perspective view of the outdoor heat exchanger of the freezing apparatus which concerns on a 2nd modification. 本発明の第２実施形態に係る冷凍装置を用いた空調機の構成図。The block diagram of the air conditioner using the freezing apparatus which concerns on 2nd Embodiment of this invention. 第２実施形態に係る冷凍装置の室内熱交換器の斜視図。The perspective view of the indoor heat exchanger of the freezing apparatus which concerns on 2nd Embodiment.

符号の説明Explanation of symbols

１１ フィン
１２ 管
３０ 室外熱交換器（蒸発器）
３１ 第１熱交換器
３２ 第２熱交換器
４０ 室内熱交換器
４１ 補助熱交換器（第１熱交換器）
４２ 主熱交換器（第２熱交換器）
１１１ 第１フィン（液側フィン）
１１２ 第２フィン（ガス側フィン） 11 Fin 12 Tube 30 Outdoor heat exchanger (evaporator)
31 1st heat exchanger 32 2nd heat exchanger 40 Indoor heat exchanger 41 Auxiliary heat exchanger (1st heat exchanger)
42 Main heat exchanger (second heat exchanger)
111 1st fin (liquid side fin)
112 2nd fin (gas side fin)

Claims (18)

分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、
複数のフィン（１１）を有する蒸発器（３０，４０）を備え、
複数の前記フィン（１１）のうち前記蒸発器（３０，４０）の冷媒入口近傍に位置するフィンのみに、着霜を防止するための着霜防止処理が施されている、
冷凍装置。 A refrigerant comprising an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure is included. A refrigeration apparatus using a non-azeotropic refrigerant mixture,
Comprising an evaporator (30, 40) having a plurality of fins (11);
Only the fin located in the vicinity of the refrigerant inlet of the evaporator (30, 40) among the plurality of fins (11) is subjected to frost prevention treatment for preventing frost formation.
Refrigeration equipment. 前記蒸発器（３０，４０）は、
前記冷媒の入口側に位置する第１熱交換器（３１，４１）と、
前記第１熱交換器（３１，４１）を通過した冷媒が流れる第２熱交換器（３２，４２）と、
を含み、
複数の前記フィン（１１）のうち前記第１熱交換器（３１，４１）側のフィンのみに前記着霜防止処理が施されている、
請求項１に記載の冷凍装置。 The evaporator (30, 40)
A first heat exchanger (31, 41) located on the refrigerant inlet side;
A second heat exchanger (32, 42) through which the refrigerant that has passed through the first heat exchanger (31, 41) flows;
Including
Of the plurality of fins (11), only the fins on the first heat exchanger (31, 41) side are subjected to the frosting prevention treatment.
The refrigeration apparatus according to claim 1. 分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、
複数のフィン（１１）を有する蒸発器（３０，４０）を備え、
複数の前記フィン（１１）のうち前記蒸発器（３０，４０）の液冷媒が存在する領域に位置するフィンのみに、着霜を防止するための着霜防止処理が施されている、
冷凍装置。 A refrigerant comprising an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure is included. A refrigeration apparatus using a non-azeotropic refrigerant mixture,
Comprising an evaporator (30, 40) having a plurality of fins (11);
Only the fin located in the area | region where the liquid refrigerant of the said evaporator (30, 40) exists among several said fins (11) is subjected to the frost formation prevention process for preventing frost formation,
Refrigeration equipment. 前記フィン（１１）は、
前記蒸発器（３０，４０）の液冷媒が存在する領域に位置する液側フィン（１１１）と、
前記蒸発器（３０，４０）のガス冷媒が存在する領域に位置するガス側フィン（１１２）と、
に分割されており、
前記液側フィン（１１１）のみに前記着霜防止処理が施されている、
請求項３に記載の冷凍装置。 The fin (11)
A liquid-side fin (111) located in a region where the liquid refrigerant of the evaporator (30, 40) exists;
A gas-side fin (112) located in a region where the gas refrigerant of the evaporator (30, 40) exists;
Is divided into
Only the liquid side fin (111) has been subjected to the frost prevention treatment,
The refrigeration apparatus according to claim 3. 前記着霜防止処理が、親水性の被膜を形成する処理である、
請求項１から請求項４のいずれか１項に記載の冷凍装置。 The anti-frosting treatment is a treatment for forming a hydrophilic film.
The refrigeration apparatus according to any one of claims 1 to 4. 前記着霜防止処理が、撥水性の被膜を形成する処理である、
請求項１から請求項４のいずれか１項に記載の冷凍装置。 The anti-frosting treatment is a treatment for forming a water-repellent film.
The refrigeration apparatus according to any one of claims 1 to 4. 前記着霜防止処理が、滑水性の被膜を形成する処理である、
請求項１から請求項４のいずれか１項に記載の冷凍装置。 The frosting prevention treatment is a treatment for forming a sliding film.
The refrigeration apparatus according to any one of claims 1 to 4. 分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、
複数のフィン（１１）を有する蒸発器（３０，４０）を備え、
複数の前記フィン（１１）のうち前記蒸発器（３０，４０）の冷媒入口近傍に位置するフィン同士の間隔が、前記冷媒入口近傍に位置しないフィン同士の間隔よりも大きい、
冷凍装置。 A refrigerant comprising an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure is included. A refrigeration apparatus using a non-azeotropic refrigerant mixture,
Comprising an evaporator (30, 40) having a plurality of fins (11);
Among the plurality of fins (11), an interval between fins located near the refrigerant inlet of the evaporator (30, 40) is larger than an interval between fins not located near the refrigerant inlet,
Refrigeration equipment. 前記蒸発器（３０，４０）は、
前記冷媒の入口側に位置する第１熱交換器（３１，４１）と、
前記第１熱交換器（３１，４１）を通過した冷媒が流れる第２熱交換器（３２，４２）と、
を含み、
複数の前記フィン（１１）のうち前記第１熱交換器（３１，４１）側のフィン同士の間隔が、前記第２熱交換器（３２，４２）側のフィン同士の間隔よりも大きい、
請求項８に記載の冷凍装置。 The evaporator (30, 40)
A first heat exchanger (31, 41) located on the refrigerant inlet side;
A second heat exchanger (32, 42) through which the refrigerant that has passed through the first heat exchanger (31, 41) flows;
Including
The space between the fins on the first heat exchanger (31, 41) side among the plurality of fins (11) is larger than the space between the fins on the second heat exchanger (32, 42) side,
The refrigeration apparatus according to claim 8. 分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、
複数のフィン（１１）を有する蒸発器（３０，４０）を備え、
複数の前記フィン（１１）のうち前記蒸発器（３０，４０）の液冷媒が存在する領域に位置するフィン同士の間隔が、前記領域に位置しないフィン同士の間隔よりも大きい、
冷凍装置。 A refrigerant comprising an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure is included. A refrigeration apparatus using a non-azeotropic refrigerant mixture,
Comprising an evaporator (30, 40) having a plurality of fins (11);
An interval between fins located in a region where the liquid refrigerant of the evaporator (30, 40) is present among the plurality of fins (11) is larger than an interval between fins not located in the region.
Refrigeration equipment. 前記フィン（１１）は、
前記蒸発器（３０，４０）の液冷媒が存在する領域に位置する液側フィン（１１１）と、
前記蒸発器（３０，４０）のガス冷媒が存在する領域に位置するガス側フィン（１１２）と、
に分割されており、
前記液側フィン（１１１）同士の間隔が、前記ガス側フィン（１１２）同士の間隔よりも大きい、
請求項１０に記載の冷凍装置。 The fin (11)
A liquid-side fin (111) located in a region where the liquid refrigerant of the evaporator (30, 40) exists;
A gas-side fin (112) located in a region where the gas refrigerant of the evaporator (30, 40) exists;
Is divided into
An interval between the liquid side fins (111) is larger than an interval between the gas side fins (112).
The refrigeration apparatus according to claim 10. 分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、
複数のフィン（１１）を有する蒸発器（３０，４０）を備え、
複数の前記フィン（１１）のうち前記蒸発器（３０，４０）の冷媒入口近傍に位置するフィンは、前記冷媒入口近傍に位置しないフィンよりも通風抵抗が小さくなるフィン形状をしている、
冷凍装置。 A refrigerant comprising an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure is included. A refrigeration apparatus using a non-azeotropic refrigerant mixture,
Comprising an evaporator (30, 40) having a plurality of fins (11);
Of the plurality of fins (11), the fins located in the vicinity of the refrigerant inlet of the evaporator (30, 40) have a fin shape with lower ventilation resistance than fins not located in the vicinity of the refrigerant inlet.
Refrigeration equipment. 前記蒸発器（３０，４０）は、
前記冷媒の入口側に位置する第１熱交換器（３１，４１）と、
前記第１熱交換器（３１，４１）を通過した冷媒が流れる第２熱交換器（３２，４２）と、
を含み、
複数の前記フィン（１１）のうち前記第１熱交換器（３１，４１）側のフィンは、前記第２熱交換器（３２，４２）側のフィンよりも通風抵抗が小さくなるフィン形状をしている、
請求項１２に記載の冷凍装置。 The evaporator (30, 40)
A first heat exchanger (31, 41) located on the refrigerant inlet side;
A second heat exchanger (32, 42) through which the refrigerant that has passed through the first heat exchanger (31, 41) flows;
Including
Of the plurality of fins (11), the fins on the first heat exchanger (31, 41) side have a fin shape with lower ventilation resistance than the fins on the second heat exchanger (32, 42) side. ing,
The refrigeration apparatus according to claim 12. 分子式がＣ3ＨmＦn（但し、ｍ＝１〜５，ｎ＝１〜５、且つｍ＋ｎ＝６）で示され且つ分子構造中に二重結合を１個有する有機化合物から成る冷媒を含む非共沸混合冷媒を用いる冷凍装置であって、
複数のフィン（１１）を有する蒸発器（３０，４０）を備え、
複数の前記フィン（１１）のうち前記蒸発器（３０，４０）の液冷媒が存在する領域に位置するフィンは、前記領域に位置しないフィンよりも通風抵抗が小さくなるフィン形状をしている、
冷凍装置。 A refrigerant comprising an organic compound having a molecular formula of C 3 H m F n (where m = 1 to 5, n = 1 to 5, and m + n = 6) and having one double bond in the molecular structure is included. A refrigeration apparatus using a non-azeotropic refrigerant mixture,
Comprising an evaporator (30, 40) having a plurality of fins (11);
Of the plurality of fins (11), the fin located in the region where the liquid refrigerant of the evaporator (30, 40) exists has a fin shape in which the ventilation resistance is smaller than that of the fin not located in the region.
Refrigeration equipment. 前記フィン（１１）は、
前記蒸発器（３０，４０）の液冷媒が存在する領域に位置する液側フィン（１１１）と、
前記蒸発器（３０，４０）のガス冷媒が存在する領域に位置するガス側フィン（１１２）と、
に分割されており、
前記液側フィン（１１１）は、前記ガス側フィン（１１２）よりも通風抵抗が小さくなるフィン形状をしている、
請求項１４に記載の冷凍装置。 The fin (11)
A liquid-side fin (111) located in a region where the liquid refrigerant of the evaporator (30, 40) exists;
A gas-side fin (112) located in a region where the gas refrigerant of the evaporator (30, 40) exists;
Is divided into
The liquid side fin (111) has a fin shape in which ventilation resistance is smaller than that of the gas side fin (112).
The refrigeration apparatus according to claim 14. 前記フィン形状は、前記冷媒が流通する管（１２）との接触部を除いて切り起しのない平板状である、
請求項１２から請求項１５のいずれか１項に記載の冷凍装置。 The fin shape is a flat plate shape that does not cut out except for a contact portion with the pipe (12) through which the refrigerant flows.
The refrigeration apparatus according to any one of claims 12 to 15. 第１熱交換器（３１，４１）及び第２熱交換器（３２，４２）が凝縮器として機能する運転が行われたとき、
前記第１熱交換器（３１，４１）は、前記第２熱交換器（３２，４２）を通過した前記冷媒を過冷却する補助熱交換器として機能する、
請求項２、請求項９、および請求項１３のいずれか１項に記載の冷凍装置。 When the first heat exchanger (31, 41) and the second heat exchanger (32, 42) are operated so as to function as a condenser,
The first heat exchanger (31, 41) functions as an auxiliary heat exchanger that supercools the refrigerant that has passed through the second heat exchanger (32, 42).
The refrigeration apparatus according to any one of claims 2, 9, and 13. 前記第２熱交換器（４２）は断面形状がほぼ逆Ｖ字状を成し、
前記第１熱交換器（４１）は、前記第２熱交換器（４２）を通過する空気流の上流側に、前記第２熱交換器（４２）に沿って配置されている、
請求項２、請求項９、および請求項１３のいずれか１項に記載の冷凍装置。 The second heat exchanger (42) has a substantially inverted V-shaped cross section,
The first heat exchanger (41) is disposed along the second heat exchanger (42) on the upstream side of the air flow passing through the second heat exchanger (42).
The refrigeration apparatus according to any one of claims 2, 9, and 13.
JP2008223837A 2008-09-01 2008-09-01 Refrigerating device Pending JP2010060159A (en)

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US9540556B2 (en) 2008-11-19 2017-01-10 The Chemours Company Fc, Llc Tetrafluoropropene compositions and uses thereof
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US9540556B2 (en) 2008-11-19 2017-01-10 The Chemours Company Fc, Llc Tetrafluoropropene compositions and uses thereof
US10208236B2 (en) 2008-11-19 2019-02-19 The Chemours Company Fc, Llc Tetrafluoropropene compositions and uses thereof
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