JP2012242032A - Refrigerator - Google Patents
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- JP2012242032A JP2012242032A JP2011114317A JP2011114317A JP2012242032A JP 2012242032 A JP2012242032 A JP 2012242032A JP 2011114317 A JP2011114317 A JP 2011114317A JP 2011114317 A JP2011114317 A JP 2011114317A JP 2012242032 A JP2012242032 A JP 2012242032A
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Abstract
Description
本発明は凝縮器をファンによって空冷する冷蔵庫において、貯留水の蒸発を促進するとともに、凝縮器の放熱能力を向上させる構造に関するものである。 The present invention relates to a structure that promotes evaporation of stored water and improves the heat dissipating ability of the condenser in a refrigerator in which the condenser is air-cooled by a fan.
省エネルギーの観点から、家庭用冷蔵庫においては筐体外郭の内側に貼り付けられて筐体外郭から自然空冷する凝縮器に加えて、ファンによって空冷する凝縮器が併用される。 From the standpoint of energy saving, a household refrigerator is used in combination with a condenser that is affixed to the inside of the outer casing and is naturally air-cooled from the outer casing.
しかしながら、家庭用冷蔵庫では省スペースの観点から、凝縮器本体や風路の大きさが制約されるとともに、室内の埃が付着するなどによって風路が閉塞される懸念が生じる。 However, in the refrigerator for home use, the size of the condenser main body and the air passage is restricted from the viewpoint of space saving, and there is a concern that the air passage is blocked due to dust adhering to the room.
そこで、省スペースや埃付着に配慮した凝縮器の設計が提案されている。特に、下部機械室を設け、凝縮器を下部機械室に設置し、底板の吸気口から外部の空気を吸引して凝縮器を空冷することで、吸気口の面積を大きくとることができるので、埃付着により風路が閉塞された場合でも、風量の低下による大幅な凝縮器の性能低下を抑制することができる。 Therefore, a condenser design that takes into account space saving and dust adhesion has been proposed. In particular, by providing a lower machine room, installing a condenser in the lower machine room, and sucking outside air from the bottom plate air intake to air-cool the condenser, the area of the air intake can be increased, Even when the air passage is blocked due to dust adhesion, it is possible to suppress a significant decrease in the performance of the condenser due to a decrease in the air volume.
また、冷蔵庫は庫内貯蔵室を冷却するため、必ず庫内空気を冷却する際に生じる除霜水を一旦下部機械室へ排水経路を通じ導き、蒸発皿に集水し、消費者がメンテナンスフリーにするため集水した貯留水を蒸発させる機構が必要となる。従来、この種の冷蔵庫の貯留水の蒸発方式は、発熱部品の冷却または放熱と共に得られる熱を蒸発皿に貯められた貯留水を蒸発させるために利用する方式を採用している。 Also, since the refrigerator cools the internal storage room, the defrost water generated when the internal air is cooled is always guided to the lower machine room through the drainage path and collected in the evaporating dish, making the maintenance-free for consumers. Therefore, a mechanism for evaporating the collected water is necessary. Conventionally, this kind of stored water evaporation method for refrigerators employs a method in which the heat obtained along with cooling or heat dissipation of the heat generating components is used to evaporate the stored water stored in the evaporating dish.
つまり、下部機械室の設計において、凝縮器の放熱能力の向上と、貯留水の蒸発能力の確保と、の両立が重要である（例えば、特許文献１参照）。 That is, in the design of the lower machine room, it is important to improve both the heat dissipation capability of the condenser and to ensure the evaporation capability of the stored water (see, for example, Patent Document 1).
以下、図面を参照しながら従来の冷蔵庫を説明する。 Hereinafter, a conventional refrigerator will be described with reference to the drawings.
図１０は、従来の冷蔵庫の下部機械室の縦断面図、図１１は、従来の冷蔵庫の下部機械室の横断面図である。 FIG. 10 is a longitudinal sectional view of a lower machine room of a conventional refrigerator, and FIG. 11 is a transverse sectional view of a lower machine room of a conventional refrigerator.
図１０において、４０は冷蔵庫の下部機械室、４１は下部機械室４０の上面を形成する貯蔵室（図示せず）の断熱壁、４２は下部機械室４０の底板、４３は下部機械室４０内に設置された凝縮器、４４は凝縮器４３を空冷するファン、４５は冷蔵庫の筐体を支える脚である。 In FIG. 10, 40 is a lower machine room of the refrigerator, 41 is a heat insulating wall of a storage room (not shown) forming the upper surface of the lower machine room 40, 42 is a bottom plate of the lower machine room 40, and 43 is in the lower machine room 40. , 44 is a fan for air-cooling the condenser 43, and 45 is a leg that supports the housing of the refrigerator.
図１１において、５０は貯蔵室（図示せず）内の除霜水を貯留する蒸発皿、５１は蒸発皿内に貯留された水を加温する浸漬配管、５２は圧縮機、５３は排出口、５４は下部機械室４０を区分する隔壁である。 In FIG. 11, 50 is an evaporating dish for storing defrosted water in a storage chamber (not shown), 51 is an immersion pipe for heating water stored in the evaporating dish, 52 is a compressor, and 53 is an outlet. , 54 are partition walls that divide the lower machine chamber 40.
ここで、凝縮器４３を冷却しながら通過した空気は隔壁５４によって蒸発皿５０の上部に集められた後、ファン４４を通過して圧縮機５２を冷却して排出口５３から外部へ排出される。このとき、蒸発皿５０の周辺は凝縮器４３と熱交換して温められた空気によって乾燥することで蒸発皿５０に貯留された水の蒸発を促進する。凝縮器４３と圧縮機５２を同一風路内に設置することで、凝縮器４３を冷却しながら通過した空気を用いて同時に圧縮機５２を冷却することができる。 Here, the air that has passed while cooling the condenser 43 is collected on the upper part of the evaporating dish 50 by the partition wall 54, then passes through the fan 44, cools the compressor 52, and is discharged from the discharge port 53 to the outside. . At this time, the periphery of the evaporating dish 50 is dried by air heated by exchanging heat with the condenser 43, thereby promoting the evaporation of water stored in the evaporating dish 50. By installing the condenser 43 and the compressor 52 in the same air path, the compressor 52 can be simultaneously cooled using the air that has passed while cooling the condenser 43.
しかしながら、前記従来の冷蔵庫の構成では、凝縮器４３の放熱に関して、圧縮機５２を下部機械室４０に納めたため、下部機械室４０内の風路形状が歪められて風路抵抗が大きくなるとともに、凝縮器４３全体に空気を流すことができず、凝縮器４３の放熱効率が低下する課題があった。 However, in the configuration of the conventional refrigerator, the compressor 52 is housed in the lower machine room 40 with respect to the heat radiation of the condenser 43, so that the air path shape in the lower machine room 40 is distorted and the air path resistance is increased. There was a problem that air could not flow through the entire condenser 43 and the heat dissipation efficiency of the condenser 43 was reduced.
また、貯留水の蒸発に関して、この種の蒸発方式の場合、水を蒸発させる因子としては大きく次の３項目がある。 Regarding the evaporation of stored water, in the case of this type of evaporation method, there are the following three items as factors for evaporating water.
第一として水面風速、第二として水温、第三として水と外気が接触する開口部面積である。 The first is the surface wind speed, the second is the water temperature, and the third is the area of the opening where water and outside air contact.
しかしながら、前記従来の構成では、凝縮器４３を通過した空気を蒸発皿５０内の水面近傍に確実に導くことができず、水面の風速が小さいために、貯留水の蒸発能力が低く、必要蒸発能力を確保するためには蒸発皿５０の開口部面積を大きくする必要があった。 However, in the conventional configuration, the air that has passed through the condenser 43 cannot be reliably guided to the vicinity of the water surface in the evaporating dish 50, and since the wind speed on the water surface is small, the evaporation capacity of the stored water is low, and the required evaporation In order to secure the capacity, it was necessary to increase the area of the opening of the evaporating dish 50.
つまり、蒸発皿５０を設置するために広いスペースが必要であり、そのために、凝縮器４３やファン４４の設置スペースに制限が生じ、凝縮器４３やファン４４の大型化によって凝縮器４３の放熱能力を向上させることができないという課題を有していた。 That is, a large space is required to install the evaporating dish 50, and therefore, the installation space of the condenser 43 and the fan 44 is limited, and the heat radiation capacity of the condenser 43 is increased by increasing the size of the condenser 43 and the fan 44. It has a problem that it cannot be improved.
本発明は、前記従来の課題を解決するもので、凝縮器の放熱能力の向上と、貯留水の蒸発能力の促進と、を簡単な構成で両立させることができる冷蔵庫を提供することを目的とする。 An object of the present invention is to solve the above-described conventional problems, and to provide a refrigerator capable of achieving both improvement of the heat dissipation capability of a condenser and promotion of evaporation capability of stored water with a simple configuration. To do.
前記従来の課題を解決するために、本発明の冷蔵庫は、下部機械室を有する冷蔵庫において、凝縮器と、前記凝縮器の風下側に設置され送風回路の主たる駆動源となるファンと、前記凝縮器の風下側に設置された蒸発皿と、を前記下部機械室内に納めるとともに、前記下部機械室の吸気口に対して前記ファンの回転中心を上方に配置し、前記ファンの回転中心に対して前記蒸発皿を下方に配置したものである。 In order to solve the above-mentioned conventional problems, the refrigerator of the present invention is a refrigerator having a lower machine room, a condenser, a fan installed on the leeward side of the condenser and serving as a main driving source of the blower circuit, and the condensation An evaporating dish installed on the leeward side of the container, and the rotation center of the fan is disposed above the intake port of the lower machine chamber, and the rotation center of the fan is The evaporating dish is disposed below.
これによって、凝縮器を通過する空気の流れを上方に向けることができ、凝縮器全体の風路抵抗を抑制し、また凝縮器を通過した温かく乾いた空気を蒸発皿の内部の水面近傍に確実に導き、水面の風速が大きくなることにより、凝縮器の放熱能力を向上させながら、貯留水の蒸発を促進することができる。 As a result, the flow of air passing through the condenser can be directed upward, the air path resistance of the entire condenser is suppressed, and the warm and dry air that has passed through the condenser is surely near the water surface inside the evaporating dish. Thus, the increase in the wind speed on the water surface can promote the evaporation of the stored water while improving the heat dissipation capability of the condenser.
本発明の冷蔵庫は、下部機械室内の風路抵抗を抑制し、凝縮器の放熱能力を向上させることができるとともに、貯留水の蒸発を促進し、蒸発皿を省スペースに配置することで、凝縮器やファンの大型化が可能となり、放熱能力を更に向上させることで省エネが図れる。 The refrigerator of the present invention suppresses the air path resistance in the lower machine room, can improve the heat dissipation capacity of the condenser, promotes evaporation of stored water, and condenses by arranging the evaporating dish in a space-saving manner. The equipment and fan can be made larger, and energy can be saved by further improving the heat dissipation capacity.
請求項１に記載の発明は、下部機械室を有する冷蔵庫において、凝縮器と、前記凝縮器の風下側に設置され送風回路の主たる駆動源となるファンと、前記凝縮器の風下側に設置された蒸発皿と、を前記下部機械室内に納めるとともに、前記下部機械室の吸気口に対して前記ファンの回転中心を上方に配置し、前記ファンの回転中心に対して前記蒸発皿を下方に配置した冷蔵庫である。これによって、凝縮器を通過する空気の流れを上方に向けることで、凝縮器全体の風路抵抗を抑制し、また凝縮器を通過した温かく乾いた空気を蒸発皿の内部の水面近傍に確実に導き、水面の風速が大きくなることにより、凝縮器の放熱能力を向上させながら、貯留水の蒸発を促進することができる。 The invention according to claim 1 is a refrigerator having a lower machine room, wherein the condenser, a fan installed on the lee side of the condenser and serving as a main drive source of the blower circuit, and installed on the lee side of the condenser. The evaporating dish is stored in the lower machine chamber, the rotation center of the fan is disposed above the intake port of the lower machine chamber, and the evaporating dish is disposed below the rotation center of the fan. Refrigerator. As a result, the flow of air passing through the condenser is directed upward, so that the air path resistance of the entire condenser is suppressed, and the warm and dry air that has passed through the condenser is reliably placed near the water surface inside the evaporating dish. In addition, by increasing the wind speed of the water surface, evaporation of the stored water can be promoted while improving the heat dissipation capability of the condenser.
請求項２に記載の発明は、下部機械室を有する冷蔵庫において、凝縮器と、前記凝縮器の風下側に設置され送風回路の主たる駆動源となるファンと、前記凝縮器の風下側に設置された蒸発皿と、を前記下部機械室内に納めるとともに、前記凝縮器を通過した空気を強制的に上方に流し、その後風路を下方に蛇行させ、前記蒸発皿の内部に空気を流す冷蔵庫である。これによって、凝縮器を通過する空気の流れを上方に向けることで、凝縮器全体の風路抵抗を抑制し、また凝縮器を通過した温かく乾いた空気を蒸発皿の内部の水面近傍に確実に導き、水面の風速が大きくなることにより、凝縮器の放熱能力を向上させながら、貯留水の蒸発を促進することができる。 The invention described in claim 2 is a refrigerator having a lower machine room, wherein the condenser, the fan installed on the lee side of the condenser and serving as a main driving source of the blower circuit, and the lee side of the condenser are installed. The evaporating dish is stored in the lower machine chamber, the air that has passed through the condenser is forced to flow upward, the air passage is then meandered downward, and the air flows into the evaporating dish. . As a result, the flow of air passing through the condenser is directed upward, so that the air path resistance of the entire condenser is suppressed, and the warm and dry air that has passed through the condenser is reliably placed near the water surface inside the evaporating dish. In addition, by increasing the wind speed of the water surface, evaporation of the stored water can be promoted while improving the heat dissipation capability of the condenser.
請求項３に記載の発明は、請求項１または２に記載の発明において、前記蒸発皿の上方に、風向板を配置した冷蔵庫である。これによって、凝縮器を通過した空気を蒸発皿の内部の水面近傍により確実に導くことができ、更に貯留水の蒸発を促進することができる。 Invention of Claim 3 is a refrigerator which has arrange | positioned the wind direction board in the invention of Claim 1 or 2 above the said evaporating dish. As a result, the air that has passed through the condenser can be reliably guided to the vicinity of the water surface inside the evaporating dish, and evaporation of the stored water can be further promoted.
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、前記凝縮器側と前記蒸発皿側を区画する隔壁と、前記隔壁に取り付けられた前記ファンと、を備え、前記隔壁のファン部にファン支え部材を配置した冷蔵庫である。これによって、下部機械室上面と隔壁との間に隙間が生じるのを防止し、ファンの風上側と風下側の空気のショートカットを抑制することができる。 Invention of Claim 4 is the invention as described in any one of Claim 1 to 3, The partition which divides the said condenser side and the said evaporating dish side, The said fan attached to the said partition, And a fan support member is disposed on the fan portion of the partition wall. Thereby, it is possible to prevent a gap from being generated between the upper surface of the lower machine room and the partition wall, and to suppress a shortcut between the air on the windward side and the leeward side of the fan.
請求項５に記載の発明は、請求項４に記載の発明において、凝縮器部と蒸発皿部を区画する隔壁と下部機械室上面との間に、緩衝部材を設けた冷蔵庫である。これによって、下部機械室上面と隔壁との隙間をシールすることで、更にファンの風上側と風下側の空気のショートカットを抑制することができるとともに、ファンの駆動音が隔壁を介して、下部機械室上面に伝播するのを防止することができる。 A fifth aspect of the present invention is the refrigerator according to the fourth aspect of the present invention, wherein a buffer member is provided between the partition wall that partitions the condenser part and the evaporating dish part and the upper surface of the lower machine room. Thus, by sealing the gap between the upper surface of the lower machine room and the partition wall, it is possible to further suppress the shortcut of the air on the windward side and leeward side of the fan, and the driving sound of the fan passes through the partition wall to Propagation to the chamber upper surface can be prevented.
請求項６に記載の発明は、請求項１から５のいずれか一項に記載の発明において、前記下部機械室内の空気の排出口の面積に対して、前記吸気口の面積を大きくした冷蔵庫である。これによって、埃付着により風路が閉塞された場合でも、風量の低下による大幅な凝縮器の性能低下を抑制することができる。 A sixth aspect of the present invention is the refrigerator according to any one of the first to fifth aspects, wherein the area of the air inlet is larger than the area of the air outlet in the lower machine room. is there. As a result, even when the air passage is blocked due to dust adhesion, it is possible to suppress a significant decrease in the performance of the condenser due to a decrease in the air volume.
以下、本発明の実施の形態について、図面を参照しながら説明するが、従来例と同一構成については同一符号を付して、その詳細な説明は省略する。なお、この実施の形態によってこの発明が限定されるものではない。 Hereinafter, embodiments of the present invention will be described with reference to the drawings, but the same reference numerals are given to the same components as those of the conventional example, and detailed description thereof will be omitted. The present invention is not limited to the embodiments.
（実施の形態１）
図１は、本発明の実施の形態１における冷蔵庫の縦断面図、図２は、同実施の形態における冷蔵庫の下部機械室の横断面図、図３は、同実施の形態における冷蔵庫の下部機械室の背面図である。
(Embodiment 1)
1 is a longitudinal sectional view of a refrigerator according to Embodiment 1 of the present invention, FIG. 2 is a transverse sectional view of a lower machine room of the refrigerator according to the embodiment, and FIG. 3 is a lower machine of the refrigerator according to the embodiment. It is a rear view of a chamber.
図１から図３において、１は冷蔵庫、２は冷蔵庫１の筐体、３は冷蔵庫１の前面に設けられた扉、４は筐体２を支える脚、５は筐体２の下部に設けられた下部機械室、６は筐体２の背面上部に設けられた上部機械室、７は上部機械室６内に納められた圧縮機、８は筐体２内部を冷却する冷却器である。 1 to 3, 1 is a refrigerator, 2 is a housing of the refrigerator 1, 3 is a door provided on the front surface of the refrigerator 1, 4 is a leg that supports the housing 2, and 5 is provided at a lower portion of the housing 2. The lower machine chamber 6 is an upper machine chamber provided at the upper back of the housing 2, 7 is a compressor housed in the upper machine chamber 6, and 8 is a cooler for cooling the inside of the housing 2.
また、１０１は筐体２の上部に配置された冷蔵室、１０２は筐体２の下部に配置された冷凍室である。 Reference numeral 101 denotes a refrigerating room arranged at the upper part of the housing 2, and 102 denotes a freezing room arranged at the lower part of the housing 2.
冷蔵室１０１は、冷蔵保存のため、凍らない程度の低い温度に維持される貯蔵室であり、具体的な温度の下限としては、通常１〜５℃に設定される。特に生鮮品の保鮮性を向上させるために温度設定を０〜１℃としている場合もある。 The refrigerated room 101 is a storage room that is kept at a low temperature that does not freeze for refrigerated storage, and the specific lower limit of the temperature is usually set to 1 to 5 ° C. In particular, the temperature may be set to 0 to 1 ° C. in order to improve the freshness of fresh products.
冷凍室１０２は、冷凍温度帯に設定される貯蔵室である。具体的には、冷凍保存のため、通常は−２２〜−１８℃に設定されるが、冷凍保存状態の向上のため、例えば−３０℃や−２５℃などの低温に設定されることもある。 The freezer compartment 102 is a storage compartment set in a freezing temperature zone. Specifically, it is usually set to −22 to −18 ° C. for frozen storage, but may be set to a low temperature such as −30 ° C. and −25 ° C. for improving the frozen storage state. .
また、９は下部機械室５内に納められた凝縮器、１０は下部機械室５を仕切る隔壁、１１は隔壁１０に取り付けられ凝縮器９を空冷する軸流ファン（ファン）、１２は下部機械室５の背面側に納められた蒸発皿、１３は空気に指向性をもたせるための風向板、１４は軸流ファン１１を支えるための軸流ファン支え部材、１５は下部機械室５の底板である。 Further, 9 is a condenser housed in the lower machine room 5, 10 is a partition that partitions the lower machine room 5, 11 is an axial fan (fan) that is attached to the partition 10 and air-cools the condenser 9, and 12 is a lower machine. An evaporating dish housed on the back side of the chamber 5, 13 is a wind direction plate for imparting directivity to the air, 14 is an axial fan support member for supporting the axial fan 11, and 15 is a bottom plate of the lower machine chamber 5. is there.
なお、隔壁１０、風向板１３、軸流ファン支え部材１４はポリプロピレンで構成されている。 The partition 10, the wind direction plate 13, and the axial fan support member 14 are made of polypropylene.
なお、凝縮器９は、埃付着による風路の閉塞を防止するために有利である、スパイラルフィンチューブ型熱交換器であり、内部を冷媒が流動する伝熱管と伝熱管の外周に螺旋状に巻き付けたフィンとから構成される。なお、本実施の形態では伝熱管は銅、フィンはアルミニウムで構成されているが、伝熱管にアルミニウムや鉄、フィンに銅や鉄などの材料を用いてもよい。 The condenser 9 is a spiral fin tube type heat exchanger that is advantageous for preventing the air passage from being blocked by dust adhering. The condenser 9 spirals around the heat transfer tube through which the refrigerant flows and the outer periphery of the heat transfer tube. Consists of wound fins. In this embodiment, the heat transfer tube is made of copper and the fin is made of aluminum. However, aluminum or iron may be used for the heat transfer tube, and copper or iron may be used for the fin.
また、１６は底板１５に設けられた空気を吸い込むための下部機械室の吸気口、１７は下部機械室５の背面側に設けられた空気を排出するための排出口である。ここで、下部機械室５は隔壁１０によって二室に分けられ、軸流ファン１１の風上側に凝縮器９、風下側に蒸発皿１２を収めている。 Reference numeral 16 denotes an intake port of the lower machine chamber for sucking air provided in the bottom plate 15, and reference numeral 17 denotes an exhaust port for discharging air provided on the back side of the lower machine chamber 5. Here, the lower machine chamber 5 is divided into two chambers by a partition wall 10, and a condenser 9 is housed on the windward side of the axial fan 11 and an evaporating dish 12 is housed on the leeward side.
なお、本実施の形態では、軸流ファン１１は蒸発皿１２側に傾けて配置している。 In the present embodiment, the axial fan 11 is disposed to be inclined toward the evaporating dish 12 side.
以上のように構成された本発明の実施の形態１における冷蔵庫について、以下その動作、作用を説明する。 About the refrigerator in Embodiment 1 of this invention comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.
圧縮機７の運転と連動して、軸流ファン１１を駆動する。軸流ファン１１の駆動によっ
て、隔壁１０で仕切られた下部機械室５の凝縮器９側が負圧となり、底板１５に設けられた吸気口１６から外部の空気を吸引し、蒸発皿１２側が正圧となり、下部機械室５内の空気を下部機械室５の背面側に設けられた排出口１７から外部へ排出する。
The axial fan 11 is driven in conjunction with the operation of the compressor 7. By driving the axial fan 11, the condenser 9 side of the lower machine chamber 5 partitioned by the partition wall 10 becomes negative pressure, external air is sucked from the intake port 16 provided in the bottom plate 15, and the evaporating dish 12 side is positive pressure. Thus, the air in the lower machine room 5 is discharged to the outside from the discharge port 17 provided on the back side of the lower machine room 5.
このとき、凝縮器９と熱交換して温められた空気によって乾燥することで蒸発皿１２に貯留された水の蒸発を促進する。 At this time, evaporation of water stored in the evaporating dish 12 is promoted by drying with air heated by heat exchange with the condenser 9.
また、圧縮機７を背面上部に設置することで、従来の下部機械室内で風路形状が蛇行するものに比べて、下部機械室５内の風路形状を直線的に簡素化することができ、下部機械室５の風路抵抗を抑制できるとともに、下部機械室５から排出される空気の温度を低減することができ、吸気口１６から再度吸気された際のショートカットの影響を防止することができる。 In addition, by installing the compressor 7 on the upper back, the air path shape in the lower machine room 5 can be simplified in a straight line as compared with the conventional one in which the air path shape meanders in the lower machine room. The air path resistance of the lower machine room 5 can be suppressed, the temperature of the air discharged from the lower machine room 5 can be reduced, and the influence of the shortcut when the air is sucked again from the intake port 16 can be prevented. it can.
また、凝縮器９全体に空気を流すことができるので、凝縮器９の放熱効率を向上させることができる。 Moreover, since air can flow through the condenser 9, the heat dissipation efficiency of the condenser 9 can be improved.
なお、下部機械室５内の風路抵抗を更に抑制するために、下部機械室５の上面１８や隔壁の曲げ部１９のＲを大きくすることが望ましい。 In order to further suppress the air path resistance in the lower machine room 5, it is desirable to increase the R of the upper surface 18 of the lower machine room 5 and the bent portion 19 of the partition wall.
また、排出口１７から排出された高温の空気が再度、吸気口１６から吸入されないように、排出口１７に排出空気を上方に向ける風向リブ３８を設けることが望ましい。 Further, it is desirable to provide a wind direction rib 38 for directing the exhaust air upward at the exhaust port 17 so that the high-temperature air exhausted from the exhaust port 17 is not sucked from the intake port 16 again.
同様に、排出口１７から吸気口１６の間で冷蔵庫１と壁の隙間を塞ぐために、冷蔵庫１の外郭に突起部を設けることが望ましい。 Similarly, in order to close the gap between the refrigerator 1 and the wall between the discharge port 17 and the intake port 16, it is desirable to provide a protrusion on the outer wall of the refrigerator 1.
このとき、下部機械室５の吸気口１６に対して軸流ファン１１の回転中心３４を上方に、軸流ファン１１の回転中心３４に対して蒸発皿１２を下方に配置し、軸流ファン１１を蒸発皿１２側に傾けて配置することで、凝縮器９を通過した空気を強制的に上方に流し、その後風路を下方に蛇行させ、蒸発皿１２内に空気を流す。これによって、凝縮器９を通過する空気の流れを上方に向けることで、凝縮器９全体の風路抵抗を抑制し、また凝縮器９を通過した温かく乾いた空気を蒸発皿１２の内部の水面近傍に確実に導き、水面の風速が大きくなることにより、凝縮器９の放熱能力を向上させながら、貯留水の蒸発を促進することができる。 At this time, the rotation center 34 of the axial fan 11 is disposed above the intake port 16 of the lower machine chamber 5, and the evaporating dish 12 is disposed below the rotation center 34 of the axial fan 11. Is inclined to the evaporating dish 12 side so that the air that has passed through the condenser 9 is forced to flow upward, and then the air path is meandered downward to cause the air to flow into the evaporating dish 12. Thereby, the flow of air passing through the condenser 9 is directed upward, so that the air path resistance of the condenser 9 as a whole is suppressed, and the warm and dry air that has passed through the condenser 9 is converted into the water surface inside the evaporating dish 12. By reliably guiding to the vicinity and increasing the wind speed on the water surface, evaporation of the stored water can be promoted while improving the heat dissipation capability of the condenser 9.
また、蒸発皿１２内の貯留水の蒸発を更に促進するために、従来の冷蔵庫と同様に、冷媒配管２０の一部を蒸発皿１２の内部に配置して、貯留水と直接熱交換してもよい。 In order to further promote the evaporation of the stored water in the evaporating dish 12, a part of the refrigerant pipe 20 is arranged inside the evaporating dish 12 and directly exchanges heat with the stored water, as in the conventional refrigerator. Also good.
なお、隔壁１０と軸流ファン１１を凝縮器９と蒸発皿１２の風下側に設置した場合、凝縮器９と軸流ファン１１の位置が離れることで、凝縮器９を通過する空気の流れが冷蔵庫１の前面から背面へ水平方向に向かうこととなり、凝縮器９の放熱能力が低下するとともに、蒸発皿１２が空気の流れを乱すことで大きな風路抵抗となり、下部機械室５の風量全体が低下する要因となる。 When the partition wall 10 and the axial fan 11 are installed on the leeward side of the condenser 9 and the evaporating dish 12, the positions of the condenser 9 and the axial fan 11 are separated, so that the air flow passing through the condenser 9 is changed. The horizontal direction from the front of the refrigerator 1 to the back is reduced, the heat dissipation capability of the condenser 9 is reduced, and the evaporating dish 12 disturbs the flow of air, resulting in a large airway resistance, and the entire air volume in the lower machine room 5 is reduced. It becomes a factor to decrease.
また、軸流ファン１１を蒸発皿１２側に傾ける角度は、底板１５に対して、１５°〜４５°程度が望ましい。軸流ファン１１を蒸発皿１２側に傾ける角度を、底板１５に対して４５°以上とすると、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができず、底板１５に対して１５°以下とすると、蒸発皿１２が下部機械室５の蒸発皿１２側の空気の流れを乱すことで大きな風路抵抗が生じ、下部機械室５の風量全体が低下する要因となる。 The angle at which the axial fan 11 is tilted toward the evaporating dish 12 is preferably about 15 ° to 45 ° with respect to the bottom plate 15. If the angle at which the axial fan 11 is tilted toward the evaporating dish 12 is 45 ° or more with respect to the bottom plate 15, the air that has passed through the condenser 9 cannot be reliably guided to the vicinity of the water surface inside the evaporating dish 12, If the bottom plate 15 is 15 ° or less, the evaporating dish 12 disturbs the flow of air on the evaporating dish 12 side of the lower machine chamber 5 to cause a large airflow resistance, and the factor that the entire air volume in the lower machine chamber 5 is reduced. It becomes.
これによって、下部機械室５内の風路抵抗の抑制による凝縮器９の放熱能力の向上と、貯留水の蒸発能力の促進と、を簡単な構成で両立することができる。 Thereby, the improvement of the heat dissipation capability of the condenser 9 by suppressing the air path resistance in the lower machine chamber 5 and the promotion of the evaporation capability of the stored water can be achieved with a simple configuration.
また、蒸発皿１２の上方に位置する隔壁のファン端部２１に、風向板１３を配置することによって、凝縮器を通過した空気を蒸発皿１２の内部の水面近傍により確実に導き、水面の風速が大きくなることにより、更に蒸発皿１２内の貯留水の蒸発を促進することができる。 In addition, by arranging the wind direction plate 13 at the fan end 21 of the partition wall located above the evaporating dish 12, the air that has passed through the condenser is reliably guided near the water surface inside the evaporating dish 12, and the wind speed of the water surface By increasing the value, evaporation of the stored water in the evaporating dish 12 can be further promoted.
なお、風向板１３の幅方向の大きさは、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができるように、蒸発皿１２の幅方向の大きさと同等以上が望ましい。 The size in the width direction of the wind direction plate 13 is equal to or larger than the size in the width direction of the evaporating dish 12 so that the air that has passed through the condenser 9 can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. Is desirable.
また、風向板１３の高さ方向の大きさについて、風向板１３の下辺の位置が軸流ファン１１の回転中心３４の高さ程度であることが望ましい。風向板１３の下辺の位置が軸流ファン１１の回転中心３４の高さ以上である場合には、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができず、風向板１３の下辺が回転中心３４の高さ以下である場合には、風向板１３が大きな風路抵抗となり、下部機械室５の風量全体が低下する要因となる。 Further, regarding the size of the wind direction plate 13 in the height direction, the position of the lower side of the wind direction plate 13 is preferably about the height of the rotation center 34 of the axial fan 11. When the position of the lower side of the wind direction plate 13 is equal to or higher than the height of the rotation center 34 of the axial fan 11, the air that has passed through the condenser 9 cannot be reliably guided to the vicinity of the water surface inside the evaporating dish 12. When the lower side of the wind direction plate 13 is less than or equal to the height of the rotation center 34, the wind direction plate 13 has a large air path resistance, which causes a reduction in the entire air volume in the lower machine room 5.
また、軸流ファン１１と隔壁１０の軸流ファン端部２１に軸流ファン支え部材１４を配置することによって、下部機械室５の上面１８と隔壁１０との間に隙間が生じるのを防止し、軸流ファン１１の風上側と風下側の空気のショートカットを抑制することができる。 Further, by disposing the axial fan support member 14 at the axial fan end 21 of the axial fan 11 and the partition wall 10, it is possible to prevent a gap from being generated between the upper surface 18 of the lower machine chamber 5 and the partition wall 10. The shortcut of the air on the windward side and the leeward side of the axial fan 11 can be suppressed.
なお、軸流ファン支え部材１４の幅方向の大きさは、軸流ファン１１の幅寸法の０．５倍以下が望ましい。軸流ファン支え部材１４の幅寸法が軸流ファン１１の０．５倍以上の場合には、軸流ファン支え部材１４が大きな風路抵抗となり、下部機械室５の風量全体が低下する要因となる。また、軸流ファン支え部材１４は隔壁１０、蒸発皿１２、または、風向板１３と一体成型してもよい。 In addition, the size in the width direction of the axial fan support member 14 is desirably 0.5 times or less the width of the axial fan 11. When the width of the axial fan support member 14 is 0.5 times or more that of the axial fan 11, the axial fan support member 14 has a large air path resistance, and the overall air volume of the lower machine chamber 5 is reduced. Become. The axial fan support member 14 may be integrally formed with the partition wall 10, the evaporating dish 12, or the wind direction plate 13.
また、下部機械室５内を区画する隔壁１０の上部と下部機械室５の上面１８との間に緩衝部材３３を設けることによって、隔壁１０と下部機械室５の上面１８との隙間をシールすることができるので、軸流ファン１１の風上側と風下側の空気がショートカットするのを更に防止することができるとともに、軸流ファン１１の駆動音が隔壁１０を介して下部機械室５の上面１８に伝播するのを防止することができる。なお、緩衝部材３３はウレタンフォーム等で構成されている。 Further, by providing a buffer member 33 between the upper portion of the partition wall 10 that partitions the lower machine chamber 5 and the upper surface 18 of the lower machine chamber 5, the gap between the partition wall 10 and the upper surface 18 of the lower machine chamber 5 is sealed. Therefore, it is possible to further prevent the air on the windward side and the leeward side of the axial flow fan 11 from being short-circuited, and the driving sound of the axial flow fan 11 passes through the partition wall 10 and the upper surface 18 of the lower machine room 5. Propagation can be prevented. The buffer member 33 is made of urethane foam or the like.
また、下部機械室５内の空気の排出口１７の面積に対して、底板１５に設けられた吸気口１６の面積を大きくするによって、埃付着により風路が閉塞された場合でも、風量の低下による大幅な凝縮器９の性能低下を抑制することができる。なお、底板１５に設けられた吸気口１６の面積は、下部機械室５内の空気の排出口１７の面積に対して、２倍程度が望ましい。 In addition, by reducing the area of the air inlet 16 provided in the bottom plate 15 relative to the area of the air outlet 17 in the lower machine room 5, the air volume is reduced even when the air passage is blocked due to dust adhesion. The significant performance degradation of the condenser 9 due to can be suppressed. The area of the air inlet 16 provided in the bottom plate 15 is preferably about twice the area of the air outlet 17 in the lower machine room 5.
（実施の形態２）
図４は、本発明の実施の形態２における冷蔵庫の下部機械室の縦断面図、図５は、同実施の形態における冷蔵庫の下部機械室の背面図である。
(Embodiment 2)
FIG. 4 is a longitudinal sectional view of the lower machine room of the refrigerator in the second embodiment of the present invention, and FIG. 5 is a rear view of the lower machine room of the refrigerator in the same embodiment.
ここでは、実施の形態１と異なる点を中心に説明する。 Here, the points different from the first embodiment will be mainly described.
図４、図５において、１１１は筐体の下部に設けられた下部機械室、２２は下部機械室１１１を仕切る隔壁、２３は隔壁２２に取り付けられ凝縮器９を空冷する軸流ファン（フ
ァン）、２４は風向板である。この風向板２４は、下部機械室１１１の上面１８から略直角に下方に向けて突出している。
4 and 5, reference numeral 111 denotes a lower machine chamber provided at the lower part of the casing, 22 denotes a partition wall that partitions the lower machine chamber 111, and 23 denotes an axial fan (fan) that is attached to the partition wall 22 and air-cools the condenser 9. , 24 are wind direction plates. The wind direction plate 24 protrudes downward from the upper surface 18 of the lower machine chamber 111 at a substantially right angle.
なお、本実施の形態では、軸流ファン２３は蒸発皿１２と反対側に傾けて配置している。より具体的には、凝縮器９側へ傾けている。 In the present embodiment, the axial fan 23 is inclined to the opposite side of the evaporating dish 12. More specifically, it is inclined toward the condenser 9 side.
以上のように構成された本発明の実施の形態２における冷蔵庫について、以下その動作、作用を説明する。 About the refrigerator in Embodiment 2 of this invention comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.
軸流ファン２３の駆動によって、隔壁２２で仕切られた下部機械室１１１の凝縮器９側が負圧となり、底板１５に設けられた複数の吸気口１６から外部の空気を吸引し、蒸発皿１２側が正圧となり、下部機械室１１１内の空気を下部機械室１１１の背面側に設けられた排出口１７から外部へ排出する。このとき、下部機械室１１１の吸気口１６に対して軸流ファン２３の回転中心３５を上方に、軸流ファン２３の回転中心３５に対して蒸発皿１２を下方に配置し、軸流ファン２３を凝縮器９側に傾けて配置することで、凝縮器９を通過する空気の流れを上方に向けることができ、凝縮器９全体の風路抵抗を抑制するとともに、高い放熱能力が得られる。 By driving the axial fan 23, the condenser 9 side of the lower machine chamber 111 partitioned by the partition wall 22 becomes negative pressure, the outside air is sucked from a plurality of intake ports 16 provided in the bottom plate 15, and the evaporating dish 12 side is A positive pressure is applied, and the air in the lower machine chamber 111 is discharged to the outside from the discharge port 17 provided on the back side of the lower machine chamber 111. At this time, the rotation center 35 of the axial fan 23 is disposed above the intake port 16 of the lower machine chamber 111, and the evaporating dish 12 is disposed below the rotation center 35 of the axial fan 23. Is inclined to the condenser 9 side, the flow of air passing through the condenser 9 can be directed upward, the air path resistance of the entire condenser 9 is suppressed, and a high heat dissipation capability is obtained.
また、蒸発皿１２の上方に風向板２４を配置することにより、凝縮器９を通過した空気を下方に蛇行させ、蒸発皿１２の内部の水面近傍に確実に空気を導くことができるので、水面の風速が大きくなり、貯留水の蒸発を促進することできる。 Further, by arranging the wind direction plate 24 above the evaporating dish 12, the air that has passed through the condenser 9 can meander downward, and the air can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. The wind speed increases and the evaporation of the stored water can be promoted.
なお、風向板２４の幅方向の大きさは、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができるように、蒸発皿１２の幅方向の大きさと同等以上が望ましい。 The size in the width direction of the wind direction plate 24 is equal to or larger than the size in the width direction of the evaporating dish 12 so that the air that has passed through the condenser 9 can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. Is desirable.
また、風向板２４の高さ方向の大きさについて、風向板２４の下辺の位置が軸流ファン２３の回転中心３５の高さ程度であることが望ましい。風向板２４の下辺の位置が軸流ファン２３の回転中心３５の高さ以上である場合には、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができず、風向板２４の下辺が回転中心３５の高さ以下である場合には、風向板２４が大きな風路抵抗となり下部機械室１１１の風量全体が低下する要因となる。 Further, regarding the size of the wind direction plate 24 in the height direction, the position of the lower side of the wind direction plate 24 is preferably about the height of the rotation center 35 of the axial fan 23. When the position of the lower side of the wind direction plate 24 is equal to or higher than the height of the rotation center 35 of the axial fan 23, the air that has passed through the condenser 9 cannot be reliably guided to the vicinity of the water surface inside the evaporating dish 12. When the lower side of the wind direction plate 24 is equal to or lower than the height of the rotation center 35, the wind direction plate 24 becomes a large wind path resistance, which causes a reduction in the entire air volume in the lower machine chamber 111.
また、風向板２４の奥行き方向の位置は、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができるように、蒸発皿１２の奥行き方向の中央よりも前方に配置するのが望ましい。 The position of the wind direction plate 24 in the depth direction is more forward than the center of the evaporating dish 12 in the depth direction so that the air that has passed through the condenser 9 can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. It is desirable to arrange.
また、下部機械室１１１内を区画する隔壁２２と下部機械室１１１の上面１８との間に緩衝部材３３を設けることによって、隔壁２２と下部機械室１１１の上面１８との隙間をシールすることができるので、軸流ファン２３の風上側と風下側の空気がショートカットするのを更に防止することができると共に、軸流ファン２３の駆動音が隔壁２２を介して下部機械室１１１の上面１８に伝播するのを防止することができる。 Further, by providing the buffer member 33 between the partition wall 22 that partitions the lower machine chamber 111 and the upper surface 18 of the lower machine chamber 111, the gap between the partition wall 22 and the upper surface 18 of the lower machine chamber 111 can be sealed. Therefore, it is possible to further prevent the air on the windward side and the leeward side of the axial flow fan 23 from being short-circuited, and the driving sound of the axial flow fan 23 propagates to the upper surface 18 of the lower machine chamber 111 via the partition wall 22. Can be prevented.
また、下部機械室１１１内の空気の排出口１７の面積に対して、底板１５に設けられた吸気口１６の面積を大きくするによって、埃付着により風路が閉塞された場合でも、風量の低下による大幅な凝縮器９の性能低下を抑制することができる。 In addition, by reducing the area of the air inlet 16 provided in the bottom plate 15 with respect to the area of the air outlet 17 in the lower machine chamber 111, the air volume is reduced even when the air passage is blocked due to dust adhesion. The significant performance degradation of the condenser 9 due to can be suppressed.
なお、底板１５に設けられた吸気口１６の面積は下部機械室１１１内の空気の排出口１７の面積に対して２倍程度が望ましい。 The area of the air inlet 16 provided in the bottom plate 15 is preferably about twice the area of the air outlet 17 in the lower machine chamber 111.
なお、本実施の形態のように、軸流ファン２３は蒸発皿１２と反対側に傾けて配置（より具体的には、凝縮器９側へ傾けている）していることにより、凝縮器９側の空気の流れをより上方に向けることで、より多くの外部の空気を取り入れて凝縮器９の放熱能力を更に向上させることができる。 Note that, as in the present embodiment, the axial fan 23 is disposed to be inclined to the opposite side of the evaporating dish 12 (more specifically, to the condenser 9 side), so that the condenser 9 By directing the air flow on the side upward, a larger amount of external air can be taken in and the heat dissipation capability of the condenser 9 can be further improved.
（実施の形態３）
図６は、本発明の実施の形態３における冷蔵庫の下部機械室の縦断面図、図７は、同実施の形態における冷蔵庫の下部機械室の背面図である。
(Embodiment 3)
FIG. 6 is a longitudinal sectional view of the lower machine room of the refrigerator according to the third embodiment of the present invention, and FIG. 7 is a rear view of the lower machine room of the refrigerator according to the same embodiment.
ここでは、実施の形態１、２と異なる点を中心に説明する。 Here, the points different from the first and second embodiments will be mainly described.
図６、図７において、２５は筐体の下部に設けられた下部機械室、２６は下部機械室２５を仕切る隔壁、２７は隔壁２６に取り付けられ凝縮器９を空冷する軸流ファン（ファン）、２８は風向板である。 6 and 7, reference numeral 25 denotes a lower machine chamber provided at the lower part of the housing, 26 denotes a partition wall that partitions the lower machine chamber 25, and 27 denotes an axial fan (fan) that is attached to the partition wall 26 and air-cools the condenser 9. , 28 are wind direction plates.
なお、本実施の形態では、軸流ファン１１は底板１５に対して、略直角方向に立設している。 In the present embodiment, the axial fan 11 is erected in a substantially perpendicular direction with respect to the bottom plate 15.
以上のように構成された本発明の実施の形態３における冷蔵庫について、以下その動作・作用を説明する。 About the refrigerator in Embodiment 3 of this invention comprised as mentioned above, the operation | movement * effect | action is demonstrated below.
軸流ファン２７の駆動によって、隔壁２６で仕切られた下部機械室２５の凝縮器９側が負圧となり、底板１５に設けられた複数の吸気口１６から外部の空気を吸引し、蒸発皿１２側が正圧となり下部機械室２５内の空気を下部機械室２５の背面側に設けられた排出口１７から外部へ排出する。このとき、下部機械室２５の吸気口１６に対して軸流ファン２７の回転中心３６を上方に、軸流ファン２７の回転中心３６に対して蒸発皿１２を下方に配置することで、凝縮器９を通過する空気の流れを上方に向けることができ、凝縮器９全体の風路抵抗を抑制するとともに、高い放熱能力が得られる。 By driving the axial fan 27, the condenser 9 side of the lower machine chamber 25 partitioned by the partition wall 26 becomes negative pressure, external air is sucked from a plurality of intake ports 16 provided in the bottom plate 15, and the evaporating dish 12 side is The air in the lower machine chamber 25 becomes positive pressure and is discharged to the outside from the discharge port 17 provided on the back side of the lower machine chamber 25. At this time, by arranging the rotation center 36 of the axial fan 27 upward with respect to the intake port 16 of the lower machine room 25 and the evaporating dish 12 downward with respect to the rotation center 36 of the axial fan 27, the condenser The air flow passing through 9 can be directed upward, the air path resistance of the entire condenser 9 is suppressed, and a high heat dissipation capability is obtained.
また、蒸発皿１２の上部に風向板２８を配置することにより、凝縮器９を通過した空気を下方に蛇行させ、蒸発皿１２の内部の水面近傍に確実に空気を導くことができるので、水面の風速が大きくなり、貯留水の蒸発を促進することできる。 Further, by disposing the wind direction plate 28 on the top of the evaporating dish 12, the air that has passed through the condenser 9 can be meandered downward, and the air can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. The wind speed increases and the evaporation of the stored water can be promoted.
なお、風向板２８の幅方向の大きさは、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができるように、蒸発皿１２の幅方向の大きさと同等以上が望ましい。 The size in the width direction of the wind direction plate 28 is equal to or larger than the size in the width direction of the evaporating dish 12 so that the air that has passed through the condenser 9 can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. Is desirable.
また、風向板２８の高さ方向の大きさについて、風向板２８の下辺の位置が軸流ファン２７の回転中心３６の高さ程度であることが望ましい。風向板２８の下辺の位置が軸流ファン２７の回転中心３６の高さ以上である場合には、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができず、風向板２８の下辺が回転中心３６の高さ以下である場合には、風向板２８が大きな風路抵抗となり下部機械室２５の風量全体が低下する要因となる。 Further, regarding the size of the wind direction plate 28 in the height direction, the position of the lower side of the wind direction plate 28 is preferably about the height of the rotation center 36 of the axial fan 27. When the position of the lower side of the wind direction plate 28 is equal to or higher than the height of the rotation center 36 of the axial fan 27, the air that has passed through the condenser 9 cannot be reliably guided to the vicinity of the water surface inside the evaporating dish 12. When the lower side of the wind direction plate 28 is equal to or less than the height of the rotation center 36, the wind direction plate 28 becomes a large wind path resistance, which causes a reduction in the entire air volume in the lower machine room 25.
また、風向板２８の奥行き方向の位置は、凝縮器９を通過した空気を蒸発皿１２の内部の水面近傍に確実に導くことができるように、蒸発皿１２の奥行き方向の中央よりも前方に配置するのが望ましい。 The position of the wind direction plate 28 in the depth direction is more forward than the center of the evaporating dish 12 in the depth direction so that the air that has passed through the condenser 9 can be reliably guided to the vicinity of the water surface inside the evaporating dish 12. It is desirable to arrange.
また、下部機械室２５内を区画する隔壁２６と下部機械室２５の上面１８との間に緩衝部材３３を設けることによって、隔壁２６と下部機械室２５の上面１８との隙間をシール
することができるので、軸流ファン２７の風上側と風下側の空気がショートカットするのを更に防止することができると共に、軸流ファン２７の駆動音が隔壁２６を介して下部機械室２５の上面１８に伝播するのを防止することができる。
Further, by providing the buffer member 33 between the partition wall 26 that partitions the lower machine chamber 25 and the upper surface 18 of the lower machine chamber 25, the gap between the partition wall 26 and the upper surface 18 of the lower machine chamber 25 can be sealed. Therefore, it is possible to further prevent the air on the leeward side and the leeward side of the axial flow fan 27 from being short-circuited, and the driving sound of the axial flow fan 27 propagates to the upper surface 18 of the lower machine room 25 via the partition wall 26. Can be prevented.
また、下部機械室２５内の空気の排出口１７の面積に対して、底板１５に設けられた吸気口１６の面積を大きくするによって、埃付着により風路が閉塞された場合でも、風量の低下による大幅な凝縮器９の性能低下を抑制することができる。なお、底板１５に設けられた吸気口１６の面積は下部機械室２５内の空気の排出口１７の面積に対して２倍程度が望ましい。 In addition, by increasing the area of the air inlet 16 provided in the bottom plate 15 relative to the area of the air outlet 17 in the lower machine room 25, the air volume is reduced even when the air passage is blocked due to dust adhesion. The significant performance degradation of the condenser 9 due to can be suppressed. The area of the air inlet 16 provided in the bottom plate 15 is preferably about twice the area of the air outlet 17 in the lower machine chamber 25.
なお、本実施の形態のように、軸流ファン２７は底板１５に対して、略直角方向に立設していることにより、下部機械室５内の風路形状をより直線的に簡素化することができ、下部機械室５の風路抵抗を抑制することで、凝縮器９の放熱能力を更に向上させることができる。 Note that, as in the present embodiment, the axial fan 27 is erected in a substantially perpendicular direction with respect to the bottom plate 15, thereby simplifying the shape of the air path in the lower machine chamber 5 more linearly. It is possible to further improve the heat dissipation capability of the condenser 9 by suppressing the air path resistance of the lower machine chamber 5.
（実施の形態４）
図８は、本発明の実施の形態４における冷蔵庫の下部機械室の縦断面図、図９は、同実施の形態における冷蔵庫の下部機械室の背面図である。
(Embodiment 4)
FIG. 8 is a longitudinal sectional view of the lower machine room of the refrigerator in the fourth embodiment of the present invention, and FIG. 9 is a rear view of the lower machine room of the refrigerator in the same embodiment.
ここでは、実施の形態１、２、３と異なる点を中心に説明する。 Here, the points different from the first, second, and third embodiments will be mainly described.
図８、図９において、２９は筐体の下部に設けられた下部機械室、３０は下部機械室２９を仕切る隔壁、３１は隔壁３０に取り付けられ凝縮器９を空冷する横断流ファン（クロスフローファン）である。 8 and 9, reference numeral 29 denotes a lower machine chamber provided in the lower part of the casing, 30 denotes a partition that partitions the lower machine chamber 29, and 31 denotes a cross-flow fan (cross flow fan that is attached to the partition 30 and cools the condenser 9 by air. Fan).
以上のように構成された本発明の実施の形態４における冷蔵庫について、以下その動作、作用を説明する。 About the refrigerator in Embodiment 4 of this invention comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.
横断流ファン３１の駆動によって、隔壁３０で仕切られた下部機械室２９の凝縮器９側が負圧となり、底板１５に設けられた複数の吸気口１６から外部の空気を吸引し、蒸発皿１２側が正圧となり下部機械室２９内の空気を下部機械室２９の背面側に設けられた排出口１７から外部へ排出する。このとき、吸気口１６に対して横断流ファン３１の回転中心３７を上方に、横断流ファン３１の回転中心３７に対して蒸発皿１２を下方に配置することで、凝縮器９を通過した空気を強制的に上方に流し、横断流ファン３１を経由して蒸発皿１２の内部に空気を流す。これによって、凝縮器９を通過する空気の流れを上方に向けることで、凝縮器９全体の風路抵抗を抑制し、また凝縮器９を通過した温かく乾いた空気を蒸発皿１２の内部の水面近傍に確実に導き、水面の風速が大きくなることにより、凝縮器９の放熱能力を向上させながら、貯留水の蒸発を促進することができる。 By driving the cross flow fan 31, the condenser 9 side of the lower machine chamber 29 partitioned by the partition wall 30 becomes negative pressure, and external air is sucked from a plurality of intake ports 16 provided in the bottom plate 15, and the evaporating dish 12 side is The air in the lower machine chamber 29 becomes positive pressure and is discharged to the outside through the discharge port 17 provided on the back side of the lower machine chamber 29. At this time, the air passing through the condenser 9 is arranged by disposing the evaporating dish 12 below the rotation center 37 of the crossflow fan 31 upward and the rotation center 37 of the crossflow fan 31 relative to the intake port 16. Is forced to flow upward, and air is caused to flow inside the evaporating dish 12 via the cross flow fan 31. Thereby, the flow of air passing through the condenser 9 is directed upward, so that the air path resistance of the condenser 9 as a whole is suppressed, and the warm and dry air that has passed through the condenser 9 is converted into the water surface inside the evaporating dish 12. By reliably guiding to the vicinity and increasing the wind speed on the water surface, evaporation of the stored water can be promoted while improving the heat dissipation capability of the condenser 9.
なお、横断流ファン３１の幅方向の大きさは、凝縮器９を通過した空気を蒸発皿１２内の水面全体に確実に流すことができるように、蒸発皿１２の幅方向の大きさと同等以上が望ましい。 The size in the width direction of the cross flow fan 31 is equal to or greater than the size in the width direction of the evaporating dish 12 so that the air that has passed through the condenser 9 can surely flow over the entire water surface in the evaporating dish 12. Is desirable.
また、横断流ファン３１の吐出口３２の位置は、凝縮器９を通過した空気を蒸発皿１２内の水面全体に確実に流すことができるように、蒸発皿１２の前方側上方が望ましい。 Further, the position of the discharge port 32 of the cross flow fan 31 is preferably above the front side of the evaporating dish 12 so that the air that has passed through the condenser 9 can flow reliably over the entire water surface in the evaporating dish 12.
また、下部機械室２９内を区画する隔壁３０と下部機械室２９の上面１８との間に緩衝部材３３を設けることによって、隔壁３０と下部機械室２９の上面１８との隙間をシールすることができるので、横断流ファン３１の風上側と風下側の空気がショートカットするのを更に防止することができると共に、横断流ファン３１の駆動音が隔壁３０を介して下
部機械室２９の上面１８に伝播するのを防止することができる。
Further, by providing the buffer member 33 between the partition wall 30 that partitions the lower machine chamber 29 and the upper surface 18 of the lower machine chamber 29, the gap between the partition wall 30 and the upper surface 18 of the lower machine chamber 29 can be sealed. Therefore, it is possible to further prevent the air on the windward side and the leeward side of the crossflow fan 31 from being short-circuited, and the driving sound of the crossflow fan 31 propagates to the upper surface 18 of the lower machine chamber 29 via the partition wall 30. Can be prevented.
また、下部機械室２９の空気の排出口１７の面積に対して、底板１５に設けられた吸気口１６の面積を大きくするによって、埃付着により風路が閉塞された場合でも、風量の低下による大幅な凝縮器の性能低下を抑制することができる。なお、底板１５に設けられた吸気口１６の面積は下部機械室２９内の空気の排出口１７の面積に対して２倍程度が望ましい。 Further, by increasing the area of the air inlet 16 provided in the bottom plate 15 with respect to the area of the air outlet 17 of the lower machine chamber 29, even when the air passage is blocked due to dust adhesion, the air volume is reduced. A significant decrease in condenser performance can be suppressed. The area of the air inlet 16 provided in the bottom plate 15 is preferably about twice the area of the air outlet 17 in the lower machine chamber 29.
なお、本実施の形態のように、横断流ファン３１を用いることにより、凝縮器９を通過した温かく乾いた空気を蒸発皿１２の幅方向全体に導くことができ、貯留水の蒸発を促進することができる。 As in the present embodiment, by using the cross flow fan 31, the warm and dry air that has passed through the condenser 9 can be guided to the entire width direction of the evaporating dish 12, and the evaporation of the stored water is promoted. be able to.
以上のように、本発明の冷蔵庫は、下部機械室を有する冷蔵庫において、凝縮器と、前記凝縮器の風下側に設置され送風回路の主たる駆動源となるファンと、前記凝縮器及び前記ファンの風下側に設置された蒸発皿と、を前記下部機械室内に納めるとともに、下部機械室の吸気口に対してファンの回転中心を上方に配置し、ファンの回転中心に対して蒸発皿を下部に配置したものである。 As described above, the refrigerator of the present invention is a refrigerator having a lower machine room, a condenser, a fan installed on the leeward side of the condenser and serving as a main driving source of the blower circuit, the condenser and the fan. The evaporating dish installed on the leeward side is housed in the lower machine room, and the rotation center of the fan is disposed above the intake port of the lower machine room, and the evaporating dish is placed below the rotation center of the fan. It is arranged.
これによって、下部機械室内の風路抵抗を抑制し、凝縮器の放熱能力を向上させることができると共に、貯留水の蒸発を促進し、蒸発皿を省スペースに配置することで、凝縮器やファンの大型化が可能になり、放熱能力を更に向上させることで省エネが図れる。 As a result, the air path resistance in the lower machine room can be suppressed and the heat dissipation capacity of the condenser can be improved, the evaporation of the stored water is promoted, and the evaporating dish is arranged in a space-saving manner, so that the condenser and fan Can be increased in size and energy can be saved by further improving the heat dissipation capability.
以上のように、本発明にかかる冷蔵庫は、凝縮器をファンによって空冷する冷蔵庫において、下部機械室内の風路抵抗を抑制し、凝縮器の放熱能力を向上させることができるとともに、貯留水の蒸発を促進し、蒸発皿を省スペースに配置することで、凝縮器やファンの大型化が可能になり、更に凝縮器の放熱能力が向上し省エネが図れるので、自動販売機など他の冷凍冷蔵応用商品にも適用できる。 As described above, in the refrigerator according to the present invention, in the refrigerator in which the condenser is air-cooled by a fan, the air path resistance in the lower machine room can be suppressed, the heat radiation capacity of the condenser can be improved, and the stored water can be evaporated. By arranging the evaporating dish in a space-saving manner, it is possible to increase the size of the condenser and fan, and further improve the heat dissipation capacity of the condenser to save energy, so that other freezing and refrigeration applications such as vending machines can be used. It can also be applied to products.
１ 冷蔵庫
２ 筐体
５、２５、２９、１１１ 下部機械室
６ 上部機械室
９ 凝縮器
１０、２２、２６、３０ 隔壁
１１、２３、２７ 軸流ファン（ファン）
１２ 蒸発皿
１３、２４、２８ 風向板
１４ 軸流ファン支え部材
１６ 吸気口
１７ 排出口
３１ 横断流ファン
３３ 緩衝部材
３４、３５、３６、３７ ファンの回転中心
DESCRIPTION OF SYMBOLS 1 Refrigerator 2 Case 5, 25, 29, 111 Lower machine room 6 Upper machine room 9 Condenser 10, 22, 26, 30 Bulkhead 11, 23, 27 Axial fan (fan)
DESCRIPTION OF SYMBOLS 12 Evaporating dish 13, 24, 28 Wind direction plate 14 Axial fan support member 16 Intake port 17 Outlet port 31 Cross flow fan 33 Buffer member 34, 35, 36, 37 Fan rotation center
Claims (6)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011114317A JP2012242032A (en) | 2011-05-23 | 2011-05-23 | Refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011114317A JP2012242032A (en) | 2011-05-23 | 2011-05-23 | Refrigerator |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2012242032A true JP2012242032A (en) | 2012-12-10 |
Family
ID=47463929
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2011114317A Pending JP2012242032A (en) | 2011-05-23 | 2011-05-23 | Refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2012242032A (en) |
Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58119178U (en) * | 1982-02-08 | 1983-08-13 | サンデン株式会社 | refrigerated case |
| JPH07146054A (en) * | 1993-11-26 | 1995-06-06 | Toshiba Corp | Refrigerator |
| US5678421A (en) * | 1995-12-26 | 1997-10-21 | Habco Beverage Systems Inc. | Refrigeration unit for cold space merchandiser |
| JPH10332253A (en) * | 1997-06-02 | 1998-12-15 | Toshiba Corp | Refrigerator |
| WO2000055554A1 (en) * | 1999-03-12 | 2000-09-21 | Matsushita Refrigeration Company | Refrigerator |
| JP2000292051A (en) * | 1999-04-01 | 2000-10-20 | Sanden Corp | Display case |
| EP1132697A2 (en) * | 2000-03-09 | 2001-09-12 | Linde Aktiengesellschaft | Water evaporating device |
| WO2005093347A1 (en) * | 2004-03-29 | 2005-10-06 | Sharp Kabushiki Kaisha | Refrigerator, sterling refrigerator, and drain water processing system |
| KR20050119454A (en) * | 2004-06-16 | 2005-12-21 | 주식회사 대우일렉트로닉스 | Defrost evaporation structure in the refrigerator |
| JP2006226654A (en) * | 2005-02-21 | 2006-08-31 | Sharp Corp | Stirling cooler |
| WO2006121347A1 (en) * | 2005-05-10 | 2006-11-16 | Skope Industries Limited | Improved refrigeration apparatus |
| JP2007064597A (en) * | 2005-09-02 | 2007-03-15 | Matsushita Electric Ind Co Ltd | Refrigerator |
| US20080223063A1 (en) * | 2007-03-12 | 2008-09-18 | Samsung Electronics Co., Ltd. | Refrigerator with air guide duct |
-
2011
- 2011-05-23 JP JP2011114317A patent/JP2012242032A/en active Pending
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS58119178U (en) * | 1982-02-08 | 1983-08-13 | サンデン株式会社 | refrigerated case |
| JPH07146054A (en) * | 1993-11-26 | 1995-06-06 | Toshiba Corp | Refrigerator |
| US5678421A (en) * | 1995-12-26 | 1997-10-21 | Habco Beverage Systems Inc. | Refrigeration unit for cold space merchandiser |
| JPH10332253A (en) * | 1997-06-02 | 1998-12-15 | Toshiba Corp | Refrigerator |
| WO2000055554A1 (en) * | 1999-03-12 | 2000-09-21 | Matsushita Refrigeration Company | Refrigerator |
| JP2000292051A (en) * | 1999-04-01 | 2000-10-20 | Sanden Corp | Display case |
| EP1132697A2 (en) * | 2000-03-09 | 2001-09-12 | Linde Aktiengesellschaft | Water evaporating device |
| WO2005093347A1 (en) * | 2004-03-29 | 2005-10-06 | Sharp Kabushiki Kaisha | Refrigerator, sterling refrigerator, and drain water processing system |
| KR20050119454A (en) * | 2004-06-16 | 2005-12-21 | 주식회사 대우일렉트로닉스 | Defrost evaporation structure in the refrigerator |
| JP2006226654A (en) * | 2005-02-21 | 2006-08-31 | Sharp Corp | Stirling cooler |
| WO2006121347A1 (en) * | 2005-05-10 | 2006-11-16 | Skope Industries Limited | Improved refrigeration apparatus |
| JP2007064597A (en) * | 2005-09-02 | 2007-03-15 | Matsushita Electric Ind Co Ltd | Refrigerator |
| US20080223063A1 (en) * | 2007-03-12 | 2008-09-18 | Samsung Electronics Co., Ltd. | Refrigerator with air guide duct |
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