JP2019138481A

JP2019138481A - refrigerator

Info

Publication number: JP2019138481A
Application number: JP2018018780A
Authority: JP
Inventors: 聡石▲崎▼; Satoshi Ishizaki; 良二河井; Ryoji Kawai; 真申小川; Masanobu Ogawa
Original assignee: Hitachi Global Life Solutions Inc
Current assignee: Hitachi Global Life Solutions Inc
Priority date: 2018-02-06
Filing date: 2018-02-06
Publication date: 2019-08-22

Abstract

To provide a refrigerator in which drying of food is not enhanced while realizing uniformization of a temperature in a cooling chamber, in the refrigerator including storage chambers of a plurality of temperature zones and including a cooler for refrigeration and a cooler for freezing.SOLUTION: In a refrigerator including a first cooling temperature zone chamber, a second cooling temperature zone chamber, and a freezing temperature zone chamber, and further including a first cooler disposed at a back portion of the first cooling temperature zone chamber, a first blower for distributing cold air of the first cooler to the first cooling temperature zone chamber, a first air trunk for allowing air to flow from the first cooler to the first cooling temperature zone chamber and returning to the first cooler, a second cooler disposed at a back portion of the freezing temperature zone chamber or the second cooling temperature zone chamber, a second blower for allowing the cold air of the second cooler to be distributed to the freezing temperature zone chamber or the second cooling temperature zone chamber, and a second air trunk for allowing the air to flow from the second cooler to the freezing temperature zone chamber or the second cooling temperature zone chamber and returning to the second cooler, a discharge port of the first air trunk is not formed on a front surface of the first cooling temperature zone chamber so that main flow cold air from the first cooler is directed to a wall surface in the first cooling temperature zone chamber.SELECTED DRAWING: Figure 2

Description

本発明は冷蔵庫に関するものである。 The present invention relates to a refrigerator.

一般的な冷蔵庫には冷蔵室，冷凍室，野菜室など，貯蔵する食品によって，適切な貯蔵温度が異なるため，複数の貯蔵室が設けられるが，そのなかでも冷蔵室は最も大きく設計されることが多い。そのため，冷蔵室内には庫内を冷却する冷気の温度分布が不均一になりやすい。そこで，特許文献1に示すように，冷蔵室庫内に冷気循環ファンを設け冷蔵室内の均温化をはかるものがある。 A general refrigerator has multiple storage rooms because the appropriate storage temperature differs depending on the food to be stored, such as a refrigerator room, a freezer room, and a vegetable room. Among them, the refrigerator room is designed to be the largest. There are many. Therefore, the temperature distribution of the cold air that cools the inside of the refrigerator is likely to be uneven in the refrigerator compartment. Therefore, as shown in Patent Document 1, there is a cooling air circulation fan provided in the refrigerator compartment so as to equalize the temperature in the refrigerator compartment.

特開２０００−８８４２２号公報JP 2000-88422 A

しかしながら，特許文献１の場合，庫内に冷気循環ファンを設けることで，食品に冷気が直接接触し，食品の乾燥が促進されてしまう。 However, in the case of Patent Document 1, by providing a cool air circulation fan in the cabinet, the cool air directly contacts the food, and the drying of the food is promoted.

前記課題を解決するために，第一冷蔵温度帯室，第二冷蔵温度帯室，冷凍温度帯室を備え，前記第一冷蔵温度帯室の背部に設けられた第一冷却器と，前記第一冷却器の冷気を前記第一冷蔵温度帯室に送風する第一送風機と，前記第一冷却器から前記第一冷蔵温度帯室を流れて前記第一冷却器に戻る第一風路と，前記冷凍温度帯室または前記第二冷蔵温度帯室の背部に設けられた第二冷却器と，前記第二冷却器の冷気を前記冷凍温度帯室または第二冷蔵温度帯室に送風する第二送風機と，前記第二冷却器から前記冷凍温度帯室または前記第二冷蔵温度帯室を流れて前記第二冷却器に戻る第二風路と，を備えた冷蔵庫において，前記第一風路の吐出口は，前記第一冷蔵温度帯室の前面には設けず，前記第一冷却器からの主流冷気が前記第一冷蔵温度帯室内の壁面に向かうことを特徴とする。 In order to solve the above-mentioned problem, a first refrigeration temperature zone chamber, a second refrigeration temperature zone chamber, a refrigeration temperature zone chamber, a first cooler provided at the back of the first refrigeration temperature zone chamber, A first blower for blowing cool air of one cooler to the first refrigeration temperature zone chamber, a first air passage from the first cooler to the first refrigeration temperature zone chamber and returning to the first cooler; A second cooler provided at the back of the refrigeration temperature zone chamber or the second refrigeration temperature zone chamber, and a second air for blowing the cool air of the second cooler to the refrigeration temperature zone chamber or the second refrigeration temperature zone chamber A refrigerator comprising: a blower; and a second air path that flows from the second cooler to the refrigeration temperature zone chamber or the second refrigeration temperature zone chamber and returns to the second cooler. The discharge port is not provided in front of the first refrigeration temperature zone, and the mainstream cold air from the first cooler is used for the first refrigeration temperature. Characterized in that it toward the wall of the band room.

本発明によれば，冷蔵用冷却器と冷凍用冷却器を備える冷蔵庫において，冷蔵室内の均温化を実現しつつも，食品の乾燥を促進させることのない冷蔵庫を提供することができる。 ADVANTAGE OF THE INVENTION According to this invention, in a refrigerator provided with the refrigerator for refrigeration and the refrigerator for freezing, the refrigerator which does not accelerate | stimulate drying of a foodstuff can be provided, implement | achieving temperature equalization in a refrigerator compartment.

本発明が適用される冷蔵庫の正面外観図である。It is a front external view of the refrigerator to which the present invention is applied. 図１に示す冷蔵庫の縦断面を示す縦断面図である。It is a longitudinal cross-sectional view which shows the longitudinal cross-section of the refrigerator shown in FIG. 図１に示す冷蔵庫の横断面を示す横断面図である。It is a cross-sectional view which shows the cross section of the refrigerator shown in FIG. 実施例に係わる冷蔵庫の風路構成を表す模式図である。It is a schematic diagram showing the air path structure of the refrigerator concerning an Example. 実施例に係わる冷蔵庫の冷凍サイクル構成を表す概略図である。It is the schematic showing the refrigerating cycle structure of the refrigerator concerning an Example. 実施例に係わる冷蔵庫の通常時の運転を表すタイムチャートの一例である。It is an example of the time chart showing the driving | running | working at the normal time of the refrigerator concerning an Example.

以下、本発明の実施形態について図面を用いて詳細に説明するが、本発明は以下の実施形態に限定されることなく、本発明の技術的な概念の中で種々の変形例や応用例をもその範囲に含むものである。 Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. However, the present invention is not limited to the following embodiments, and various modifications and application examples are included in the technical concept of the present invention. Is also included in the range.

＜第１の実施形態＞
本発明に係る冷蔵庫の実施例について説明する。まず，実施例に係る冷蔵庫の構成を図１〜図５を参照しながら説明する。図１は実施例に係る冷蔵庫の正面図，図２は図１のＡ−Ａ断面図，図３は図２のＢ−Ｂ断面図，図４は実施例に係る冷蔵庫の風路構成を示す模式図，図５は実施例に係る冷蔵庫の冷凍サイクルの構成を表す概略図である。冷蔵庫１の断熱箱体１０は，前方に開口しており，上方から冷蔵室２（第一冷蔵温度帯室），左右に並設された製氷室３と上段冷凍室４，下段冷凍室５，野菜室６（第二冷蔵温度帯室）の順に貯蔵室を形成している。以下では，製氷室３，上段冷凍室４，下段冷凍室５は，まとめて冷凍室７（冷凍温度帯室）と呼ぶ。 <First Embodiment>
An embodiment of the refrigerator according to the present invention will be described. First, the structure of the refrigerator which concerns on an Example is demonstrated, referring FIGS. 1 is a front view of a refrigerator according to the embodiment, FIG. 2 is a sectional view taken along line AA in FIG. 1, FIG. 3 is a sectional view taken along line BB in FIG. FIG. 5 is a schematic diagram illustrating the configuration of the refrigeration cycle of the refrigerator according to the embodiment. The heat insulating box 10 of the refrigerator 1 is opened forward, and from above the refrigerator compartment 2 (first refrigerator temperature zone), the ice making compartment 3 and the upper freezer compartment 4, the lower freezer compartment 5, arranged side by side on the left and right. A storage room is formed in the order of the vegetable room 6 (second refrigeration temperature zone room). Hereinafter, the ice making room 3, the upper freezing room 4, and the lower freezing room 5 are collectively referred to as a freezing room 7 (freezing temperature zone room).

冷蔵室２の前方の開口は，左右に分割された回転式の冷蔵室扉２ａ，２ｂにより開閉され，製氷室３，上段冷凍室４，下段冷凍室５，野菜室６の前方の開口は，引き出し式の製氷室扉３ａ，上段冷凍室扉４ａ，下段冷凍室扉５ａ，野菜室扉６ａによってそれぞれ開閉される。冷蔵室扉２ａ，２ｂの庫内側外周には，シール部材として冷蔵室パッキン９５a，９５ｂ（第一シール部材），製氷室扉３ａ，上段冷凍室扉４ａ，下段冷凍室扉５ａの庫内側外周には，シール部材として冷凍室パッキン９６a，９６ｂ，９６ｃ（第二シール部材），野菜室６の扉である野菜室扉６ａの庫内側外周には，シール部材として野菜室パッキン９７（第三シール部材）をそれぞれ備えており，各扉を閉じた際に，断熱箱体１０の前縁部と接触することにより庫内外の空気の流通を抑制するようにしている。冷蔵室パッキン９５a，９５ｂの周長はそれぞれ２２７１ｍｍ，２４４１ｍｍであり冷蔵室パッキン９５a，９５ｂの全周長（第一シール部材の周長）は４７１２ｍｍである。冷凍室パッキン９６a，９６ｂ，９６ｃの周長は，それぞれ９７６ｍｍ，１４１６ｍｍ，２０８７ｍｍであり，冷凍室パッキン９6a，９6ｂ，96cの全周長（第二シール部材の周長）は４２０９ｍｍである。また，野菜室パッキン９７の周長（第三シール部材の周長）は２１０７ｍｍである。 The front opening of the refrigerating room 2 is opened and closed by rotary refrigerating room doors 2a and 2b divided into left and right, and the front opening of the ice making room 3, the upper freezing room 4, the lower freezing room 5, and the vegetable room 6 is The drawer-type ice making room door 3a, the upper freezer compartment door 4a, the lower freezer compartment door 5a, and the vegetable compartment door 6a are opened and closed. Refrigerator compartment packings 95a and 95b (first seal members), ice making door 3a, upper freezer compartment door 4a, and lower freezer compartment door 5a are provided on the outer perimeter of refrigerator compartment doors 2a and 2b. Is a freezer compartment packing 96a, 96b, 96c (second seal member) as a seal member, and a vegetable compartment packing 97 (third seal member) as a seal member on the inner periphery of the vegetable compartment door 6a which is a door of the vegetable compartment 6. When the doors are closed, the flow of air inside and outside the cabinet is suppressed by contacting the front edge of the heat insulating box 10. The peripheral lengths of the refrigerator compartment packings 95a and 95b are 2271 mm and 2441 mm, respectively, and the total peripheral length of the refrigerator compartment packings 95a and 95b (peripheral length of the first seal member) is 4712 mm. The peripheral lengths of the freezer compartment packings 96a, 96b, and 96c are 976 mm, 1416 mm, and 2087 mm, respectively, and the total peripheral lengths of the freezer compartment packings 96a, 96b, and 96c (the peripheral length of the second seal member) are 4209 mm. Moreover, the perimeter of the vegetable compartment packing 97 (perimeter of the third seal member) is 2107 mm.

冷蔵庫１と扉２ａ，２ｂを固定するために扉ヒンジ（図示せず）は冷蔵室２上部及び下部に設けてあり，上部の扉ヒンジは扉ヒンジカバー１６で覆われている。また，扉２ａには庫内の温度設定の操作を行う操作部９９を設けている。 In order to fix the refrigerator 1 and the doors 2a and 2b, door hinges (not shown) are provided at the upper and lower parts of the refrigerator compartment 2, and the upper door hinges are covered with a door hinge cover 16. The door 2a is provided with an operation unit 99 for performing an operation for setting the temperature in the cabinet.

冷蔵室２の温度と，冷凍室７の温度は，操作部９９を介してユーザーが維持温度レベルを選択できるようになっている。具体的には，冷蔵室２と冷凍室７の維持温度レベルの設定はそれぞれ「強」「中」「弱」の３段階に設定できるようになっており，冷蔵室２は「強」では約２℃，「中」では約４℃，「弱」では約６℃に維持され，冷凍室７は「強」では約-２２℃，「中」では約−２０℃，「弱」では約−１８℃に維持される。なお，野菜室６は平均的に７℃程度に維持される。 The temperature of the refrigerator compartment 2 and the temperature of the freezer compartment 7 can be selected by the user via the operation unit 99. Specifically, the setting of the maintenance temperature level of the refrigerator compartment 2 and the freezer compartment 7 can be set in three stages of “strong”, “medium”, and “weak”, respectively. 2 ° C, “Medium” is maintained at about 4 ° C., “Low” is maintained at about 6 ° C., and the freezer room 7 is “High” at about −22 ° C., “Medium” at about −20 ° C. Maintained at 18 ° C. The vegetable room 6 is maintained at about 7 ° C. on average.

冷蔵庫１の幅ＷはＷ＝６８５ｍｍ（図１参照），奥行きＤはＤ＝７３８ｍｍ（図２参照），高さＨはＨ＝１８３３ｍｍ（図１参照）であり，断熱箱体１０の開口部における冷蔵室高さ寸法ＨＲはＨＲ＝７８７ｍｍ，冷凍室高さ寸法ＨＦはＨＦ＝４８２ｍｍ，野菜室高さ寸法ＨＶはＨＶ＝３３４ｍｍである（図２参照）。ＪＩＳＣ９８０１−３：２０１５に基づく全定格内容積は６０２Lであり，内訳は冷蔵室が３０８Ｌであり全定格内容積の５１．２％，冷凍室は１８０Ｌであり２９．９％（全定格内容積の２８％以上），野菜室は１１４Ｌであり全定格内容積の１８．９％である。 The width W of the refrigerator 1 is W = 685 mm (see FIG. 1), the depth D is D = 738 mm (see FIG. 2), and the height H is H = 1833 mm (see FIG. 1). The refrigerator compartment height dimension HR is HR = 787 mm, the freezer compartment height dimension HF is HF = 482 mm, and the vegetable compartment height dimension HV is HV = 334 mm (see FIG. 2). The total rated internal volume based on JISC9801-3: 2015 is 602L, the breakdown is 308L for the refrigerator compartment, 51.2% of the total rated internal volume, the freezer compartment is 180L, 29.9% (of the total rated internal volume) 28% or more), the vegetable compartment is 114L, which is 18.9% of the total rated internal volume.

図２に示すように，外箱１０ａと内箱１０ｂとの間に発泡断熱材（例えば発泡ウレタン）を充填して形成される断熱箱体１０により，冷蔵庫１の庫外と庫内は隔てられている。断熱箱体１０には発泡断熱材に加えて複数の真空断熱材３６を，鋼板製の外箱１０ａと合成樹脂製の内箱１０ｂとの間に実装している。冷蔵室２と，上段冷凍室４及び製氷室３は断熱仕切壁２８（空気流通遮断手段）によって隔てられ，下段冷凍室５と野菜室６は断熱仕切壁２９によって隔てられている。また，製氷室３，上段冷凍室４，及び下段冷凍室５の各貯蔵室の前面側には，扉３ａ，４ａ，５ａの隙間を介した庫内外の空気の流通を防ぐために，断熱仕切壁３０を設けている。 As shown in FIG. 2, the outside of the refrigerator 1 and the inside of the refrigerator 1 are separated by a heat insulating box 10 formed by filling a foam heat insulating material (for example, urethane foam) between the outer box 10 a and the inner box 10 b. ing. In addition to the foam heat insulating material, a plurality of vacuum heat insulating materials 36 are mounted on the heat insulating box 10 between a steel plate outer box 10a and a synthetic resin inner box 10b. The refrigerator compartment 2, the upper freezer compartment 4 and the ice making compartment 3 are separated by a heat insulating partition wall 28 (air circulation blocking means), and the lower freezer compartment 5 and the vegetable compartment 6 are separated by a heat insulating partition wall 29. In addition, a heat insulating partition wall is provided on the front side of each storage room of the ice making room 3, the upper freezing room 4, and the lower freezing room 5 in order to prevent the flow of air inside and outside the space through the gaps of the doors 3a, 4a, 5a. 30 is provided.

冷蔵室２の扉２ａ，２ｂの庫内側には上方に開口した複数の扉ポケット３３ａ，３３ｂ，３３ｃと，複数の棚３４ａ，３４ｂ，３４ｃ，３４ｄを設け，複数の貯蔵スペースに区画されている。なお，最上部の扉ポケット３３aの開口高さ（図２中の破線）は最上段の棚３４aよりも高い位置に設けられている。冷凍室７及び野菜室６には，それぞれ扉３ａ，４ａ，５ａ，６ａと一体に引き出される製氷室容器（図示せず），上段冷凍室容器４ｂ，下段冷凍室容器５ｂ，野菜室容器６ｂを備えている。野菜室容器６ｂは，上下２段に分かれており，下段側の前方には飲料のボトル類を収納できるボトル収納スペース６ｃを備えている。ボトル収納スペース６ｃの高さ寸法は，１．５Ｌや２Ｌの飲料のボトルを立てて収納できるように３０５ｍｍ以上確保している（本実施例では３１５ｍｍ）。また，飲料用のボトルを収納可能なことは，カタログや取扱説明書，広告媒体等の文面，図，写真，映像を通じてユーザーに周知される。 A plurality of door pockets 33a, 33b, 33c opened upward and a plurality of shelves 34a, 34b, 34c, 34d are provided on the inner side of the doors 2a, 2b of the refrigerator compartment 2 and partitioned into a plurality of storage spaces. . The opening height (broken line in FIG. 2) of the uppermost door pocket 33a is provided at a position higher than that of the uppermost shelf 34a. The freezer compartment 7 and the vegetable compartment 6 are respectively provided with an ice making container (not shown), an upper freezer container 4b, a lower freezer container 5b, and a vegetable compartment container 6b that are pulled out integrally with the doors 3a, 4a, 5a, 6a. I have. The vegetable compartment container 6b is divided into two upper and lower tiers, and a bottle storage space 6c is provided in front of the lower tier for storing beverage bottles. The height of the bottle storage space 6c is 305 mm or more (315 mm in this embodiment) so that 1.5L and 2L beverage bottles can be stood and stored. Also, the ability to store beverage bottles is made known to users through catalogs, instruction manuals, texts such as advertising media, diagrams, photographs, and videos.

断熱仕切壁２８の上方には，冷蔵室２の温度帯より低めに設定可能なチルドルーム３５を設けている。チルドルーム３５は，ユーザーが操作部９９を介して設定温度を選択することができる。具体的には，冷蔵温度帯の約０〜３℃に維持する「温度レベル１」と，冷凍温度帯の約−３〜０℃に維持する「温度レベル２」の何れかに設定することができる。 A chilled room 35 that can be set lower than the temperature range of the refrigerator compartment 2 is provided above the heat insulating partition wall 28. In the chilled room 35, the user can select a set temperature via the operation unit 99. Specifically, it can be set to either “temperature level 1” maintained at about 0 to 3 ° C. of the refrigeration temperature zone or “temperature level 2” maintained at about −3 to 0 ° C. of the refrigeration temperature zone. it can.

冷蔵室２の略背部には冷蔵用冷却器室８ａを備えており，冷蔵用冷却器室８ａ内には，フィンチューブ式熱交換器である冷蔵用冷却器１４ａ(第一冷却器)が収納されている。冷蔵用冷却器１４ａの上方には冷蔵用ファン９ａ（第一送風機）を備えている。また，冷蔵室２背部の幅方向の略中心には冷蔵室送風路１１を備えており，冷蔵室送風路１１の上部には，吹き出す空気を上方に指向させる指向手段を備えた冷蔵室吐出口１１ａを備えている。なお，本実施例の冷蔵庫では，冷蔵室吐出口１１ａの指向手段として，冷蔵室吐出口１１ａの開口面を上方に向けている。冷蔵室吐出口１１ａから上方に向けて吹き出された冷却空気は，図２中に矢印で示すように冷蔵室２の天井面を沿って流れて冷蔵室２の前方の領域に到達し，棚３４a，３４ｂ，３４ｃの前方に生じる扉ポケット３３a，３３ｂ，３３ｃとの隙間を流れ，棚３４ｃと棚３４ｄの間の空間の左後方に設けられた開口９２（図３参照）を介してチルドルーム３５の後方空間に入り，冷蔵用冷却器室８ａの下部前面，下部左側面，下部右前面に設けられた冷蔵室戻り風路１５ａ，１５ｂ，１５ｃ（図３参照）から冷蔵用冷却器室８ａに戻る。また，棚３４ｃと棚３４ｄの間の空間を流れた空気の一部は，棚３４ｃと棚３４ｄの間の空間の右後方に設けられた冷蔵室戻り風路１５ｄ（図３参照）から冷蔵用冷却器室８ａに戻る。なお，冷蔵室戻り風路１５ｃの一部には，冷蔵室２を流れる空気と接するように脱臭部材９１（一例としてオープンセル構造脱臭部材）を備えている。 A refrigerating cooler chamber 8a is provided substantially at the back of the refrigerating chamber 2, and a refrigerating cooler 14a (first cooler), which is a fin-tube heat exchanger, is accommodated in the refrigerating cooler chamber 8a. Has been. A refrigeration fan 9a (first blower) is provided above the refrigeration cooler 14a. Further, a refrigerator compartment air passage 11 is provided at a substantially center in the width direction of the back of the refrigerator compartment 2, and a refrigerator outlet having an orientation means for directing the air to be blown upward is provided above the refrigerator compartment air passage 11. 11a. In the refrigerator of the present embodiment, the opening surface of the refrigerator compartment discharge port 11a is directed upward as the directing means of the refrigerator compartment discharge port 11a. The cooling air blown upward from the refrigerating chamber discharge port 11a flows along the ceiling surface of the refrigerating chamber 2 as shown by an arrow in FIG. 2, reaches the area in front of the refrigerating chamber 2, and reaches the shelf 34a. , 34b, 34c flows through the gaps between the door pockets 33a, 33b, 33c, and the chilled room 35 through an opening 92 (see FIG. 3) provided at the left rear of the space between the shelf 34c and the shelf 34d. To the refrigeration cooler chamber 8a from the refrigeration chamber return air passages 15a, 15b, 15c (see FIG. 3) provided in the lower front, lower left side, and lower right front of the refrigeration cooler chamber 8a. Return. Further, a part of the air flowing through the space between the shelf 34c and the shelf 34d is used for refrigeration from the refrigerator compartment return air passage 15d (see FIG. 3) provided at the right rear of the space between the shelf 34c and the shelf 34d. Return to the cooler chamber 8a. A part of the refrigerating room return air passage 15c is provided with a deodorizing member 91 (open cell structure deodorizing member as an example) so as to be in contact with the air flowing through the refrigerating room 2.

このような風路構成とすることで，冷蔵用冷却器１４ａから吐出された冷気は棚に収納された食品に直接接触することなく流通するため，食品の乾燥を促進させることなく，冷蔵室２内を冷却することができる。なお，本実施例の吐出口１１ａは上方を開口として，冷気を上方の壁面に当てる構成としているが，開口の位置は上方に限定されるものではなく，吐出口の開口を左右方向として，冷気を左右の側壁面に当てる構成であっても，上記目的は達成される。また，前面にわずかに開口があったとしても，上方の開口面積が前面の開口面積に対して十分に大きく，主流冷気が冷蔵室２の天面に向かうものであれば，上記目的は達成される。 By adopting such an air path configuration, the cold air discharged from the refrigerator 14a for refrigeration circulates without directly contacting the food stored in the shelf. Therefore, the refrigerator 2 is not promoted to dry the food. The inside can be cooled. The discharge port 11a of the present embodiment is configured so that the upper side is an opening and cool air is applied to the upper wall surface. However, the position of the opening is not limited to the upper side. Even if it is the structure which hits to the side wall surface on either side, the said objective is achieved. Even if there is a slight opening on the front surface, the above object can be achieved if the upper opening area is sufficiently large relative to the opening area on the front surface and the mainstream cold air is directed to the top surface of the refrigerator compartment 2. The

また，本実施例では，冷蔵用冷却器１４ａから吐出された冷気が，冷蔵室２内の天面を沿って前面側へ流れ，冷蔵室２の扉２ａ，２ｂの上方から扉ポケット３３ａの開口部へ至り易くなるので，扉ポケット３３ａ内を速やかに冷却できる効果がある。 Further, in this embodiment, the cold air discharged from the refrigeration cooler 14a flows to the front side along the top surface in the refrigeration chamber 2, and the door pocket 33a is opened from above the doors 2a and 2b of the refrigeration chamber 2. Therefore, the interior of the door pocket 33a can be quickly cooled.

冷凍室７の略背部には冷凍用冷却器室８ｂを備えており，冷凍用冷却器室８ｂ内には，フィンチューブ式熱交換器である冷凍用冷却器１４ｂ（第二冷却器）が収納されている。冷凍用冷却器１４ｂの上方には冷凍用ファン９ｂを備えている。また，冷凍室７の背部には冷凍室送風路１２を備えており，冷凍用ファン９ｂ（第二送風機）の前方の冷凍室送風路１２には複数の冷凍室吐出口１２ａを備えている。冷凍室用冷却器室８ｂの下部前方には冷凍室７に送られた空気が戻る冷凍室戻り風路１７（図２及び図３参照）を備えている。 A refrigeration cooler chamber 8b is provided substantially at the back of the freezer compartment 7, and a refrigeration cooler 14b (second cooler), which is a fin-tube heat exchanger, is accommodated in the refrigeration cooler chamber 8b. Has been. A refrigeration fan 9b is provided above the refrigeration cooler 14b. A freezer compartment air passage 12 is provided at the back of the freezer compartment 7, and a plurality of freezer compartment discharge ports 12 a are provided in the freezer compartment air passage 12 in front of the freezing fan 9 b (second blower). A freezer compartment return air passage 17 (see FIGS. 2 and 3) through which the air sent to the freezer compartment 7 returns is provided in front of the lower portion of the freezer compartment cooler chamber 8b.

野菜室６への風路となる野菜室送風路１３は，冷凍室送風路１２の右下方から分岐形成され，断熱仕切壁２９を通過している。野菜室送風路１３の出口となる野菜室吐出口１３aは，野菜室６背部右上の断熱仕切壁２９下面の高さと略一致するように設けられ，下方に開口している。野菜室送風路１３には，野菜室６の冷却制御手段である野菜室ダンパ１９を備えている（図３参照）。野菜室６と冷凍室７の間の断熱仕切壁２９の左下部前方には，野菜室戻り流入口１８ａを備えており，断熱仕切壁２９内を通過する野菜室戻り風路１８を介して冷凍用冷却器室８ｂの下部前方に設けられた野菜室戻り流出口１８ｂに至る流路が形成されている。 The vegetable room air passage 13 serving as an air passage to the vegetable room 6 is branched from the lower right side of the freezer compartment air passage 12 and passes through the heat insulating partition wall 29. The vegetable room discharge port 13a serving as the outlet of the vegetable room air passage 13 is provided so as to substantially coincide with the height of the lower surface of the heat insulating partition wall 29 at the upper right of the back of the vegetable room 6 and opens downward. The vegetable room air passage 13 is provided with a vegetable room damper 19 which is a cooling control means for the vegetable room 6 (see FIG. 3). A vegetable room return inlet 18a is provided in front of the lower left part of the heat insulating partition wall 29 between the vegetable room 6 and the freezing room 7 and is frozen through the vegetable room return air passage 18 passing through the heat insulating partition wall 29. A flow path reaching the vegetable room return outlet 18b provided in front of the lower part of the cooler room 8b is formed.

次に，本実施例に係る冷蔵庫の風路構成について図４を参照しながら説明する。冷蔵用冷却器１４ａと熱交換して低温になった空気は，冷蔵用ファン９ａを駆動することにより，冷蔵室送風路１１，冷蔵室吐出口１１ａを介して冷蔵室２に送風され，冷蔵室２内を冷却する。冷蔵室２に送られた空気は，冷蔵室戻り風路１５ａ，１５ｂ，１５ｃ及び１５ｄ（図３参照）から冷蔵用冷却器室８ａに戻る。以下，この冷蔵用冷却器室８aから冷蔵室２を流れて冷蔵用冷却器室８aに戻る風路を冷蔵風路１１１（第一風路）と呼ぶ。また，冷凍用冷却器１４ｂと熱交換して低温になった空気は，冷凍用ファン９ｂを駆動することにより，冷凍室送風路１２，冷凍室吐出口１２ａを介して冷凍室７に送風され，冷凍室７内を冷却する。冷凍室７に送られた空気は，冷凍室戻り風路１７から冷凍用冷却器室８ｂに戻る。また，野菜室ダンパ１９が開放状態の場合には，冷凍室送風路１２に流入した冷却空気の一部が野菜室送風路１３を流れ，野菜室吐出口１３ａを介して野菜室６に至り，野菜室６内を冷却する。野菜室６に送られた空気は，野菜室戻り風路１８を流れて冷凍用冷却器室８ｂに戻る。以下，この冷凍用冷却器室８ｂから冷凍室７を流れて冷凍用冷却器室８ｂに戻る風路と，冷凍用冷却器室８ｂから野菜室６を流れて冷凍用冷却器室８ｂに戻る風路を冷凍野菜風路１１２（第二風路）と呼ぶ。 Next, the air path configuration of the refrigerator according to the present embodiment will be described with reference to FIG. The air cooled to the low temperature by exchanging heat with the refrigeration cooler 14a is blown to the refrigeration room 2 via the refrigeration room air passage 11 and the refrigeration room outlet 11a by driving the refrigeration fan 9a. 2 is cooled. The air sent to the refrigerating room 2 returns to the refrigerating cooler room 8a from the refrigerating room return air passages 15a, 15b, 15c and 15d (see FIG. 3). Hereinafter, the air path that flows from the refrigerating cooler chamber 8a through the refrigerating chamber 2 and returns to the refrigerating cooler chamber 8a is referred to as a refrigerating air path 111 (first air path). Further, the air that has become low temperature by heat exchange with the freezer cooler 14b is sent to the freezer compartment 7 through the freezer compartment air passage 12 and the freezer compartment discharge port 12a by driving the freezer fan 9b. The inside of the freezer compartment 7 is cooled. The air sent to the freezer compartment 7 returns from the freezer compartment return air passage 17 to the freezer cooler compartment 8b. In addition, when the vegetable compartment damper 19 is in an open state, a part of the cooling air flowing into the freezer compartment air passage 12 flows through the vegetable compartment air passage 13 and reaches the vegetable compartment 6 through the vegetable compartment discharge port 13a. Cool the vegetable compartment 6. The air sent to the vegetable compartment 6 flows through the vegetable compartment return air passage 18 and returns to the refrigeration cooler compartment 8b. Hereinafter, the air path that flows from the freezer cooler chamber 8b to the freezer cooler chamber 8b through the freezer chamber 7b, and the wind that flows from the freezer cooler chamber 8b to the freezer cooler chamber 8b through the vegetable chamber 6 The road is called a frozen vegetable air path 112 (second air path).

本実施例の冷蔵庫では，冷蔵用ファン９ａは翼径が１００ｍｍの遠心ファン（後向きファン）であり，冷凍用ファン９ｂは翼径が１１０ｍｍの軸流ファン（プロペラファン）である。遠心ファンは軸方向から吸込んだ空気を９０度転向して径方向に吹き出す特性を有する。一方，軸流ファンは軸方向から吸込んだ空気を軸方向に吹き出す特性を有する。したがって，軸方向に吸込んだ流れを９０度転向させる風路では，遠心ファンが実装性に優れ，軸方向に吸込んだ流れを軸方向に吹き出す風路では軸流ファンが実装性に優れる。従って，冷蔵用ファン９ａとしては，前方から吸込んだ空気を，９０度転向して上方の冷蔵室送風路１１に吹き出す構成となるため，遠心ファンである後向きファンを採用し，冷凍用ファン９ｂとしては，後方から吸込んだ空気を前方の冷凍室送風路１２に吹き出す構成となるために，軸流ファンであるプロペラファンを採用してスペース効率が高い冷蔵庫としている。 In the refrigerator of the present embodiment, the refrigeration fan 9a is a centrifugal fan (backward fan) having a blade diameter of 100 mm, and the refrigeration fan 9b is an axial fan (propeller fan) having a blade diameter of 110 mm. The centrifugal fan has a characteristic that the air sucked from the axial direction is turned 90 degrees and blown out in the radial direction. On the other hand, the axial fan has a characteristic of blowing out air sucked from the axial direction in the axial direction. Therefore, the centrifugal fan is excellent in mountability in the air passage that turns the flow sucked in the axial direction by 90 degrees, and the axial fan is excellent in mountability in the air passage that blows out the flow sucked in the axial direction in the axial direction. Accordingly, since the refrigeration fan 9a is configured to turn the air sucked from the front 90 degrees and blow it out to the upper refrigeration chamber air passage 11, a rearward fan, which is a centrifugal fan, is adopted as the refrigeration fan 9b. Has a configuration in which the air sucked from the rear is blown out to the front freezer compartment air passage 12, so that a propeller fan, which is an axial fan, is used to provide a highly space-efficient refrigerator.

図２及び図３に示すように，冷蔵室２，冷凍室７，野菜室６の庫内背面側には，冷蔵室温度センサ４１，冷凍室温度センサ４２，野菜室温度センサ４３を備え，それぞれ冷蔵室２，冷凍室７，野菜室６の温度を検知している。また，冷蔵用冷却器１４ａの上部には冷蔵用冷却器温度センサ４０ａ，冷凍用冷却器１４ｂの上部には冷凍用冷却器温度センサ４０ｂを備え，冷蔵用冷却器１４ａ，及び冷凍用冷却器１４ｂの温度を検知している。また，冷蔵庫１の天井部の扉ヒンジカバー１６の内部には，外気（庫外空気）の温度，湿度を検知する外気温湿度センサ３７を備え，扉２ａ，２ｂ，３ａ，４ａ，５ａ，６ａには，開閉状態をそれぞれ検知する扉センサ（不図示）を備えている。 As shown in FIG.2 and FIG.3, the refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, and the vegetable compartment temperature sensor 43 are provided on the back side in the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6 respectively. The temperature of the refrigerator compartment 2, the freezer compartment 7, and the vegetable compartment 6 is detected. Further, a refrigeration cooler temperature sensor 40a is provided above the refrigeration cooler 14a, and a refrigeration cooler temperature sensor 40b is provided above the refrigeration cooler 14b, and the refrigeration cooler 14a and the refrigeration cooler 14b are provided. The temperature is detected. Further, inside the door hinge cover 16 on the ceiling of the refrigerator 1 is provided with an outside air temperature / humidity sensor 37 for detecting the temperature and humidity of the outside air (outside air), and the doors 2a, 2b, 3a, 4a, 5a, 6a. Are provided with door sensors (not shown) for detecting the open / closed state.

また，冷凍用冷却器室８ｂの下部には，冷凍用冷却器１４ｂを加熱する除霜ヒータ２１を備えている。除霜ヒータ２１は，例えば５０Ｗ〜２００Ｗの電気ヒータで，本実施例では１５０Ｗのラジアントヒータを設けている。冷凍用冷却器１４ｂの除霜時に発生した除霜水（融解水）は，冷凍用冷却器室８ｂの下部に備えた樋２３ｂに流下し，排水口２２ｂ，冷凍用排水管２７ｂを介して冷蔵庫１の後方（背面側）下部に設けられた機械室３９に至り，機械室３９内に設置された圧縮機２４の上部の蒸発皿３２に排出される。 Further, a defrosting heater 21 for heating the refrigeration cooler 14b is provided below the refrigeration cooler chamber 8b. The defrost heater 21 is, for example, an electric heater of 50 W to 200 W, and a 150 W radiant heater is provided in this embodiment. The defrost water (melted water) generated at the time of defrosting the refrigeration cooler 14b flows down into the tub 23b provided at the lower part of the refrigeration cooler chamber 8b, and is stored in the refrigerator via the drain port 22b and the refrigeration drain pipe 27b. 1 reaches the machine room 39 provided at the lower part of the rear (back side), and is discharged to the evaporating dish 32 above the compressor 24 installed in the machine room 39.

また，冷蔵用冷却器１４ａの除霜方法については後述するが，冷蔵用冷却器１４ａの除霜時に発生した除霜水は，冷蔵用冷却器室８ａの下部に備えた樋２３ａに流下し，排水口２２ａ，冷蔵用排水管２７ａを介して圧縮機２４の上部に備えた蒸発皿３２に排出される。 Further, although the defrosting method of the refrigeration cooler 14a will be described later, the defrost water generated at the time of defrosting the refrigeration cooler 14a flows down to the eaves 23a provided at the lower part of the refrigeration cooler chamber 8a, It is discharged to the evaporating dish 32 provided on the upper part of the compressor 24 through the drain port 22a and the refrigeration drain pipe 27a.

機械室３９内には，上述の圧縮機２４，蒸発皿３２とともに，フィンチューブ式熱交換器である庫外放熱器５０a，庫外ファン２６を備えている。庫外ファン２６の駆動により圧縮機２４，庫外放熱器５０a蒸発皿３２に空気が流れ，圧縮機２４と庫外放熱器５０aからの放熱が促進され，省エネルギー性能を高めるとともに，蒸発皿３２に通風することで，蒸発皿３２に溜まった除霜水の蒸発を促進して溢水を抑制し，信頼性を高めている。 In the machine room 39, the above-described compressor 24 and evaporating dish 32 are provided, as well as an outside heat radiator 50a and an outside fan 26 that are fin-tube heat exchangers. By driving the external fan 26, air flows into the compressor 24 and the external radiator 50a evaporating dish 32, heat dissipation from the compressor 24 and the external radiator 50a is promoted, energy saving performance is improved, and By ventilating, the evaporation of defrosted water accumulated in the evaporating dish 32 is promoted to suppress overflow and improve reliability.

図３に示すように，樋２３ａには，樋２３ａにおいて凍結した除霜水を融解させる樋ヒータ１０１を備えている。また，冷蔵用排水管２７ａには排水管上部ヒータ１０２及び排水管下部ヒータ１０３を備えている。なお，樋ヒータ１０１，排水管上部ヒータ１０２，排水管下部ヒータ１０３は，何れも除霜ヒータ２１よりも容量が低いヒータであり，本実施例では樋ヒータ１０１を６Ｗ，排水管上部ヒータ１０２を３Ｗ，排水管下部ヒータ１０３を１Ｗとしている。 As shown in FIG. 3, the eaves 23 a includes an eaves heater 101 that melts the defrost water frozen in the eaves 23 a. The refrigeration drain pipe 27 a includes a drain pipe upper heater 102 and a drain pipe lower heater 103. The dredge heater 101, the drain pipe upper heater 102, and the drain pipe lower heater 103 are all heaters having a capacity lower than that of the defrost heater 21. In this embodiment, the dredge heater 101 is 6 W and the drain pipe upper heater 102 is 3W, drain pipe lower heater 103 is 1W.

ここで，冷蔵用ファン９ａを駆動すると，冷蔵用冷却器室８ａの右上に設けられた冷蔵室戻り口１５ｂを介して，冷蔵室２からの戻り空気を樋２３ａに向けて下方に流し，樋２３ａを加熱して温度を上げるようにしている。これにより，樋２３ａにおいて凍結した除霜水を融解させる樋ヒータ１０１の加熱量を低減する効果が得られ，省エネルギー性能を高めることができる。 Here, when the refrigeration fan 9a is driven, the return air from the refrigeration chamber 2 flows downward toward the tub 23a through the refrigeration chamber return port 15b provided in the upper right of the refrigeration cooler chamber 8a. 23a is heated to raise the temperature. Thereby, the effect of reducing the heating amount of the firewood heater 101 that melts the defrosted water frozen in the firewood 23a is obtained, and the energy saving performance can be enhanced.

また，排水管２７ａ下部は，冷凍室７及び冷凍用冷却器室８ｂよりも外箱１０ａに近接させている。これにより，排水管２７ａにおいて凍結した除霜水を融解させる排水管下部ヒータ１０３の加熱量を低減することができ，省エネルギー性能が高くなる。 The lower portion of the drain pipe 27a is closer to the outer box 10a than the freezer compartment 7 and the freezer cooler compartment 8b. Thereby, the heating amount of the drain pipe lower heater 103 for melting the defrost water frozen in the drain pipe 27a can be reduced, and the energy saving performance is improved.

冷蔵庫１の天井部（図２参照）には，制御装置の一部であるＣＰＵ，ＲＯＭやＲＡＭ等のメモリ，インターフェース回路等を搭載した制御基板３１を配置している。制御基板３１は，冷蔵室温度センサ４１，冷凍室温度センサ４２，野菜室温度センサ４３，冷却器温度センサ４０ａ，４０ｂ等と接続され，前述のＣＰＵは，これらの出力値や操作部９９の設定，前述のＲＯＭに予め記録されたプログラム等を基に，圧縮機２４や冷蔵用ファン９ａ，冷凍用ファン９ｂのＯＮ／ＯＦＦや回転速度制御，除霜ヒータ２１，樋ヒータ１０１，排水管上部ヒータ１０２，排水管下部ヒータ１０３，及び，後述する三方弁５２の制御等を行っている。 On the ceiling of the refrigerator 1 (see FIG. 2), a control board 31 on which a CPU, a memory such as a ROM and a RAM, an interface circuit, etc., which are a part of the control device are mounted. The control board 31 is connected to the refrigerator compartment temperature sensor 41, the freezer compartment temperature sensor 42, the vegetable compartment temperature sensor 43, the cooler temperature sensors 40a, 40b, etc., and the CPU described above sets these output values and the operation unit 99. , Based on a program or the like recorded in advance in the ROM, the compressor 24, the refrigeration fan 9a, the refrigeration fan 9b ON / OFF and the rotational speed control, the defrost heater 21, the soot heater 101, the drain pipe upper heater 102, the drain pipe lower heater 103, and a three-way valve 52, which will be described later, are controlled.

図５は，実施例１に係る冷蔵庫の冷凍サイクル（冷媒流路）である。本実施例の冷蔵庫１では，圧縮機２４（押除量９．２ｃｃ），冷媒の放熱を行う庫外放熱器５０ａと壁面放熱配管５０ｂ，断熱仕切壁２８，２９，３０の前縁部への結露を抑制する結露抑制配管５０ｃ（庫外放熱器５０ａ，庫外放熱器５０ｂ，結露抑制配管５０ｃを放熱手段と呼ぶ），冷媒流制御手段である三方弁５２，冷媒を減圧させる減圧手段である冷蔵用キャピラリチューブ５３ａ，冷凍用キャピラリチューブ５３ｂ，冷媒と庫内の空気を熱交換させて，庫内の熱を吸熱する冷蔵用冷却器１４ａ，及び，冷凍用冷却器１４ｂを備えている。また，三方弁５２の上流には，冷凍サイクル中の水分を除去するドライヤ５１を備え，冷蔵用冷却器１４ａの下流と，冷凍用冷却器１４ｂの下流には，それぞれ液冷媒が圧縮機２４に流入するのを防止する冷蔵用気液分離器５４ａ，冷凍用気液分離器５４ｂを備えている。さらに冷凍用気液分離器５４ｂの下流には逆止弁５６を備えている。これらの構成要素を冷媒配管により接続することで冷凍サイクルを構成している。なお本実施例の冷蔵庫においては，冷蔵用冷却器１４a及び冷凍用冷却器１４ｂの温度を，圧縮機２４，冷蔵用ファン９a，冷凍用ファン９ｂの回転速度によって調整するため，圧縮機２４，冷蔵用ファン９a，冷凍用ファン９ｂを冷却器温度調整手段と呼ぶ。また，冷媒には可燃性冷媒のイソブタンを用いており，冷媒量封入量は８８ｇである。 FIG. 5 is a refrigeration cycle (refrigerant flow path) of the refrigerator according to the first embodiment. In the refrigerator 1 of the present embodiment, the compressor 24 (pushing amount 9.2 cc), the external heat radiator 50a that radiates the refrigerant, the wall surface heat radiating pipe 50b, and the front edges of the heat insulating partition walls 28, 29, and 30 are provided. Condensation suppression piping 50c that suppresses condensation (external heat radiator 50a, external heat radiator 50b, and condensation suppression piping 50c are referred to as heat dissipation means), a three-way valve 52 that is a refrigerant flow control means, and a pressure reduction means that decompresses the refrigerant. A refrigeration capillary tube 53a, a refrigeration capillary tube 53b, a refrigeration cooler 14a that absorbs heat in the storage by exchanging heat between the refrigerant and the air in the storage, and a refrigeration cooler 14b are provided. Further, a dryer 51 for removing moisture in the refrigeration cycle is provided upstream of the three-way valve 52, and liquid refrigerant is supplied to the compressor 24 downstream of the refrigeration cooler 14a and downstream of the refrigeration cooler 14b, respectively. A refrigeration gas / liquid separator 54a and a refrigeration gas / liquid separator 54b for preventing the inflow are provided. Further, a check valve 56 is provided downstream of the refrigeration gas-liquid separator 54b. A refrigeration cycle is configured by connecting these components through refrigerant piping. In the refrigerator of this embodiment, the temperature of the refrigeration cooler 14a and the refrigeration cooler 14b is adjusted by the rotational speed of the compressor 24, the refrigeration fan 9a, and the refrigeration fan 9b. The cooling fan 9a and the freezing fan 9b are referred to as cooler temperature adjusting means. In addition, flammable refrigerant isobutane is used as the refrigerant, and the amount of refrigerant enclosed is 88 g.

三方弁５２は，流出口５２ａと，流出口５２ｂを備えており，流出口５２ａを開放状態，流出口５２ｂを閉鎖状態として，冷蔵用キャピラリチューブ５３ａ側に冷媒を流す状態１（冷蔵モード），流出口５２ａを閉鎖状態，流出口５２ｂを開放状態として，冷凍用キャピラリチューブ５３ｂ側に冷媒を流す状態２（冷凍モード），及び，流出口５２ａ，５２ｂの何れも閉鎖状態とする状態３（全閉モード）を備えた冷媒流制御弁である。 The three-way valve 52 includes an outflow port 52a and an outflow port 52b. With the outflow port 52a in an open state and the outflow port 52b in a closed state, the refrigerant flows into the chilling capillary tube 53a side 1 (refrigeration mode), State 2 (freezing mode) in which the outlet 52a is closed and the outlet 52b is opened, and the refrigerant flows to the freezing capillary tube 53b side, and state 3 (all the outlets 52a and 52b are closed) (Closed mode).

三方弁５２が状態１（冷蔵モード）に制御されている場合，圧縮機２４から吐出した冷媒は，庫外放熱器５０ａ，庫外放熱器５０ｂ，結露抑制配管５０ｃを流れて放熱し，ドライヤ５１を介して三方弁５２に至る。三方弁５２は状態１（流出口５２ａが開放状態，流出口５２ｂが閉鎖状態）となっているため，続いて，冷媒は冷蔵用キャピラリチューブ５３ａを流れて減圧され冷蔵用冷却器１４ａに至り，冷蔵室２の戻り空気と熱交換する。冷蔵用冷却器１４ａを出た冷媒は，冷蔵用気液分離器５４ａを通り，キャピラリチューブ５３ａとの接触部５７ａを流れることでキャピラリチューブ５３ａ内を流れる冷媒と熱交換した後に圧縮機２４に戻る。 When the three-way valve 52 is controlled in the state 1 (refrigeration mode), the refrigerant discharged from the compressor 24 flows through the external heat radiator 50a, the external heat radiator 50b, and the dew condensation suppression pipe 50c to radiate heat, and the dryer 51 To the three-way valve 52. Since the three-way valve 52 is in the state 1 (the outlet 52a is in the open state and the outlet 52b is in the closed state), the refrigerant flows through the refrigeration capillary tube 53a and is depressurized to reach the refrigeration cooler 14a. Heat exchange with the return air of the refrigerator compartment 2 is performed. The refrigerant that has exited the refrigeration cooler 14a passes through the refrigeration gas-liquid separator 54a, flows through the contact portion 57a with the capillary tube 53a, exchanges heat with the refrigerant flowing in the capillary tube 53a, and then returns to the compressor 24. .

三方弁５２が状態２（冷凍モード）に制御されている場合，圧縮機２４から吐出した冷媒は，庫外放熱器５０ａ，庫外放熱器５０ｂ，結露抑制配管５０ｃを流れて放熱し，ドライヤ５１を介して三方弁５２に至る。三方弁５２は状態２（流出口５２ａが閉鎖状態，流出口５２ｂが開放状態）となっているため，続いて，冷媒は冷凍用キャピラリチューブ５３ｂを流れて減圧されて低温化し，冷凍用冷却器１４ｂで，冷凍室７の戻り空気及び野菜室６の戻り空気（野菜室ダンパ１９が開放状態の場合）と熱交換する。冷凍用冷却器１４ｂを出た冷媒は，冷凍用気液分離器５４ｂを通り，キャピラリチューブ５３ｂとの接触部５７ｂを流れることでキャピラリチューブ５３ｂ内を流れる冷媒と熱交換した後に圧縮機２４に戻る。 When the three-way valve 52 is controlled to the state 2 (refrigeration mode), the refrigerant discharged from the compressor 24 flows through the external heat radiator 50a, the external heat radiator 50b, and the dew condensation suppression pipe 50c to radiate heat, and the dryer 51 To the three-way valve 52. Since the three-way valve 52 is in the state 2 (the outlet 52a is closed and the outlet 52b is open), the refrigerant flows through the refrigeration capillary tube 53b and is depressurized to lower the temperature. In 14b, heat exchange is performed with the return air of the freezer compartment 7 and the return air of the vegetable compartment 6 (when the vegetable compartment damper 19 is in an open state). The refrigerant that has exited the refrigeration cooler 14b passes through the refrigeration gas-liquid separator 54b, flows through the contact portion 57b with the capillary tube 53b, exchanges heat with the refrigerant flowing in the capillary tube 53b, and then returns to the compressor 24. .

三方弁５２が状態３（全閉モード）に制御されている場合，圧縮機２４を駆動すると，冷蔵用キャピラリチューブ５３ａ，冷凍用キャピラリチューブ５３ｂから冷媒が供給されない状態となるため，冷蔵用冷却器１４ａ内の冷媒，または，冷凍用冷却器１４ｂ内の冷媒が放熱手段側に回収される（詳細は後述）。 When the three-way valve 52 is controlled to the state 3 (fully closed mode), when the compressor 24 is driven, the refrigerant is not supplied from the refrigeration capillary tube 53a and the refrigeration capillary tube 53b. The refrigerant in 14a or the refrigerant in the refrigeration cooler 14b is collected on the heat radiating means side (details will be described later).

本実施例の冷蔵庫は，三方弁５２を状態１（冷蔵モード）に制御し，圧縮機２４を駆動状態，冷蔵用ファン９ａを駆動状態，冷凍用ファン９ｂを停止状態とすることで冷蔵室２を冷却する「冷蔵運転」，三方弁５２を状態２（冷凍モード）に制御し，圧縮機２４を駆動状態，野菜室ダンパ１９を開放状態，冷蔵用ファン９ａを駆動状態，または停止状態，冷凍用ファン９ｂを駆動状態とすることで冷凍室７と野菜室６を冷却する「冷凍野菜運転」，三方弁５２を状態２（冷凍モード）に制御し，圧縮機２４を駆動状態，野菜室ダンパ１９を閉鎖状態，冷蔵用ファン９ａを駆動状態または停止状態，冷凍用ファン９ｂを駆動状態とすることで冷凍室７を冷却する「冷凍運転」，三方弁５２を状態３（全閉モード）に制御し，圧縮機２４を駆動状態として，冷蔵用冷却器１４ａ内の冷媒，または，冷凍用冷却器１４ｂ内の冷媒を放熱手段側に回収する「冷媒回収運転」，三方弁５２を状態３（全閉モード）として圧縮機２４を停止状態，冷蔵用ファン９ａを停止状態，冷凍用ファン９ｂを停止状態とする「運転停止」，三方弁５２を状態２（冷凍モード）且つ圧縮機２４を駆動状態に制御，または，三方弁５２を状態３（全閉モード）且つ圧縮機２４を停止状態に制御して，冷蔵用冷却器１４ａに冷媒が流れない状態として冷蔵用ファンを駆動状態として，冷蔵用冷却器１４ａの表面に成長した霜や冷却器自体の蓄冷熱で冷蔵室２を冷却しつつ冷蔵用冷却器１４ａの除霜を行う「冷蔵用冷却器除霜運転」，三方弁５２を状態３（全閉モード）として圧縮機２４を停止状態，冷蔵用ファン９ａを駆動状態または停止状態，冷凍用ファン９ｂを停止状態，除霜ヒータ２１を通電状態とすることで，冷凍用冷却器１４ｂの除霜を行う「冷凍用冷却器除霜運転」の各運転を適宜実施することで，冷蔵庫１の庫内各貯蔵室を冷却する。 In the refrigerator of this embodiment, the three-way valve 52 is controlled to be in state 1 (refrigeration mode), the compressor 24 is driven, the refrigeration fan 9a is driven, and the refrigeration fan 9b is stopped. “Refrigeration operation” for cooling the refrigerator, the three-way valve 52 is controlled to state 2 (freezing mode), the compressor 24 is driven, the vegetable compartment damper 19 is opened, the refrigeration fan 9a is driven or stopped, "Frozen vegetable operation" that cools the freezer compartment 7 and the vegetable compartment 6 by setting the fan 9b in the driving state, the three-way valve 52 is controlled to the state 2 (freezing mode), the compressor 24 is driven, and the vegetable compartment damper 19 is closed, refrigeration fan 9a is driven or stopped, and refrigeration fan 9b is driven to “freeze operation” to cool freezer compartment 7, and three-way valve 52 is set to state 3 (fully closed mode). Control and drive compressor 24 "Refrigerant recovery operation" in which the refrigerant in the refrigeration cooler 14a or the refrigerant in the refrigeration cooler 14b is recovered to the heat radiating means side, and the three-way valve 52 is in state 3 (fully closed mode). “Stop operation” in which the refrigeration fan 9a is stopped and the refrigeration fan 9b is stopped, the three-way valve 52 is controlled to the state 2 (refrigeration mode) and the compressor 24 is driven, or the three-way valve 52 is stopped. Is controlled in the state 3 (fully closed mode) and the compressor 24 is stopped, and the refrigerant is not flowing into the refrigeration cooler 14a, the refrigeration fan is driven, and the surface of the refrigeration cooler 14a is grown. Compressor with “refrigeration cooler defrosting operation” for defrosting refrigeration cooler 14a while refrigeration chamber 2 is cooled by frost or the regenerator heat of cooler itself, with three-way valve 52 in state 3 (fully closed mode) 24 is stopped, refrigeration fan Each operation of the “refrigeration cooler defrosting operation” in which the refrigerating cooler 14 b is defrosted by setting “a” to the driving state or the stopped state, the refrigerating fan 9 b to the stopped state, and the defrosting heater 21 to be energized. As appropriate, each storage room in the refrigerator 1 is cooled.

図６は本実施例に係る冷蔵庫を，３２℃，相対湿度７０％の環境下に設置し，通常運転モードによる安定冷却運転が行われている状態を表すタイムチャートである。なお冷蔵室２の維持温度レベルは「中」，冷凍室７の維持温度レベルは「中」，チルドルーム３５は「温度レベル１」に設定されている。 FIG. 6 is a time chart showing a state where the refrigerator according to the present embodiment is installed in an environment of 32 ° C. and a relative humidity of 70% and a stable cooling operation is performed in the normal operation mode. The maintenance temperature level of the refrigerator compartment 2 is set to “medium”, the maintenance temperature level of the freezer compartment 7 is set to “medium”, and the chilled room 35 is set to “temperature level 1”.

経過時間ｔ_０は冷蔵室２を冷却する冷蔵運転が開始された経過時間である。通常運転モードにおける冷蔵運転では，三方弁５２が状態１（冷蔵モード）に制御され，圧縮機２４が速度１（８００min^-1）で駆動されて冷蔵用冷却器１４ａに冷媒が供給されることで，冷蔵用冷却器１４ａの温度が低下している。この状態で冷蔵用ファン９ａが速度２（１５００min^-1）で駆動されることで，冷蔵用冷却器１４ａを通過して低温になった空気が冷蔵室吐出口１１a（図２参照）から冷蔵室２内に吹き出し，冷蔵室２が冷却されて温度が低下している。 Elapsed time t ₀ is the elapsed time refrigerating operation for cooling the refrigerating compartment 2 is started. In the refrigeration operation in the normal operation mode, the three-way valve 52 is controlled to the state 1 (refrigeration mode), the compressor 24 is driven at a speed 1 (800 min ⁻¹ ), and the refrigerant is supplied to the refrigeration cooler 14a. The temperature of the refrigeration cooler 14a is decreasing. In this state, the refrigeration fan 9a is driven at a speed of 2 (1500 min ⁻¹ ), so that the low temperature air passing through the refrigeration cooler 14a passes through the refrigeration chamber discharge port 11a (see FIG. 2). The refrigeration chamber 2 is cooled and the temperature is lowered.

ここで，冷蔵運転中の冷蔵用冷却器１４ａの時間平均温度は−６℃であり，後述する冷凍運転中の冷凍用冷却器１４ｂの時間平均温度の-２４℃よりも高くしている。一般に冷却器温度（蒸発温度）が高い方が，冷凍サイクル成績係数（圧縮機２４の入力に対する吸熱量の割合）が高く，省エネルギー性能が高い。冷凍室７は冷凍温度に維持するために冷凍用冷却器１４ｂの温度を低温にする必要があるが，冷蔵室２は冷蔵温度に維持すれば良いので，冷蔵用冷却器１４ａの温度を高めるように冷蔵用ファン９a及び圧縮機２４の回転速度を制御して，省エネルギー性能を向上している。経過時間ｔ_１で冷蔵室温度センサ４１が検知する冷蔵室温度T_Rが冷蔵運転終了温度Ｔ_{Ｒ＿ｏｆｆ}まで低下したことで，冷蔵運転から冷媒回収運転に切換わっている。冷媒回収運転では三方弁５２が状態３（全閉モード）に制御され，圧縮機２４が速度１（８００min^-1），冷蔵用ファン９aが速度２（１５００min^-1）で駆動されて，冷蔵用冷却器１４ａ内の冷媒が２分間回収される（ΔＴ_Ａ１＝２min）。これにより，次の冷凍野菜運転及び冷凍運転での冷媒不足による冷却効率低下を抑制することができる。なお，このとき冷蔵用ファン９ａが駆動されることで，冷蔵用冷却器１４ａ内の残留冷媒が冷蔵室２の冷却に活用されるとともに，冷蔵室２内の空気による加熱で，冷蔵用冷却器１４ａ内の圧力低下が緩和される。これにより，圧縮機２４の吸込冷媒の比体積増加が抑制され，比較的短い時間で多くの冷媒を回収できるようになり，冷却効率を高めることができる。 Here, the time average temperature of the refrigerating cooler 14a during the refrigerating operation is −6 ° C., which is higher than the time average temperature −24 ° C. of the refrigerating cooler 14b during the refrigerating operation described later. In general, the higher the cooler temperature (evaporation temperature), the higher the coefficient of performance of the refrigeration cycle (the ratio of the endothermic amount to the input of the compressor 24), and the higher the energy saving performance. In order to maintain the freezing room 7 at the freezing temperature, it is necessary to lower the temperature of the freezing cooler 14b. However, since the freezing room 2 only needs to be maintained at the freezing temperature, the temperature of the freezing cooler 14a is increased. In addition, the rotational speed of the refrigeration fan 9a and the compressor 24 is controlled to improve the energy saving performance. Elapsed time by the refrigerating compartment temperature T _R of the refrigerating compartment temperature sensor 41 at t ₁ is detected is decreased to refrigerating operation end temperature T _{R_off,} it is switched to the refrigerant recovery run from refrigerating operation. In the refrigerant recovery operation, the three-way valve 52 is controlled to state 3 (fully closed mode), the compressor 24 is driven at speed 1 (800 min ⁻¹ ), and the refrigeration fan 9a is driven at speed 2 (1500 min ⁻¹ ). The refrigerant in the cooler 14a is recovered for 2 minutes (ΔT _A1 = 2 min). Thereby, the cooling efficiency fall by the refrigerant | coolant shortage by the following frozen vegetable driving | operation and freezing driving | operation can be suppressed. At this time, when the refrigeration fan 9a is driven, the residual refrigerant in the refrigeration cooler 14a is utilized for cooling the refrigeration chamber 2, and the refrigeration cooler is heated by the air in the refrigeration chamber 2. The pressure drop in 14a is alleviated. As a result, an increase in the specific volume of the suction refrigerant of the compressor 24 is suppressed, and a large amount of refrigerant can be recovered in a relatively short time, thereby improving the cooling efficiency.

冷媒回収運転が終わると（経過時間ｔ_２），冷蔵用冷却器除霜運転を実施するかが判定され，ここではチルドルーム３５の設定が「温度レベル１」となっているため，冷蔵用ファン９aが速度１（９００min^-1）で駆動されて冷蔵用冷却器除霜運転が行われている。これにより冷蔵用冷却器１４ａの温度が上昇するとともに，霜や冷蔵用冷却器１４aの蓄冷熱による冷却効果によって，冷蔵室２の温度上昇が緩和される。このように冷蔵用冷却器の除霜運転を行い，冷蔵用ファンを駆動するモードを備えることで，冷蔵用ファンの駆動時間は，後述する冷凍用ファンの駆動時間よりも長く，また，長時間冷蔵室内の空気を循環することとなり，冷蔵室庫内の均温化を図ることができる。 When the refrigerant recovery operation ends (elapsed time t ₂ ), it is determined whether or not the refrigeration cooler defrosting operation is performed. Here, since the setting of the chilled room 35 is “temperature level 1”, the refrigeration fan 9a is driven at a speed of 1 (900 min ⁻¹ ), and the refrigeration cooler defrosting operation is performed. As a result, the temperature of the refrigerating cooler 14a rises, and the temperature rise of the refrigerating chamber 2 is mitigated by the cooling effect due to frost and the regenerative heat of the refrigerating cooler 14a. By providing a mode for performing the defrosting operation of the refrigeration cooler and driving the refrigeration fan in this way, the drive time of the refrigeration fan is longer than the drive time of the refrigeration fan described later, The air in the refrigerator compartment is circulated, so that the temperature inside the refrigerator compartment can be equalized.

また経過時間ｔ_２で冷凍室温度センサ４２が検知する冷凍室温度Ｔ_Ｆが，冷凍野菜運転開始温度Ｔ_{Ｆ_ｏｎ}以上となっていることから冷凍野菜運転が開始され，野菜室６が冷却され野菜室温度Ｔ_Ｖが低下している。冷凍野菜運転では，三方弁５２が状態２（冷凍モード）に制御され，圧縮機２４が速度２（１４００min^-1）で駆動されて冷凍用冷却器１４ｂに冷媒が供給されて，冷凍用冷却器１４ｂが低温になる。この状態で野菜室ダンパ１９が開放され，冷凍用ファン９ｂが速度１（１２００min^-1）で駆動されることで，冷凍用冷却器１４ｂを通過して低温になった空気で冷凍室７と野菜室６が冷却される。 The freezing compartment temperature T _F of the freezing compartment temperature sensor 42 detects the elapsed time t ₂ is, frozen vegetables driving frozen vegetables operation since the start has a temperature T _{F_on} above is started, the vegetable compartment vegetable compartment 6 is cooled temperature _{T V} is decreased. In the frozen vegetable operation, the three-way valve 52 is controlled to the state 2 (freezing mode), the compressor 24 is driven at the speed 2 (1400 min ⁻¹ ), and the refrigerant is supplied to the freezing cooler 14b. 14b becomes low temperature. In this state, the vegetable compartment damper 19 is opened, and the freezing fan 9b is driven at a speed of 1 (1200 min ^-1 ), so that the air that has passed through the freezing cooler 14b and has been cooled to the freezing compartment 7 and the vegetable Chamber 6 is cooled.

経過時間ｔ_３で野菜室温度センサ４３が検知する野菜室温度T_Ｖが野菜室冷却終了温度Ｔ_{Ｖ＿ｏｆｆ}に到達したことにより，野菜室ダンパ１９が閉鎖され，冷凍運転に移行している。 By vegetable compartment temperature T _V of vegetable compartment temperature sensor 43 at elapsed time t ₃ detects reaches the vegetable compartment cooling end temperature T _{V_off,} it closed vegetable compartment damper 19 has shifted to the freezing operation.

経過時間ｔ_４で冷凍室温度センサ４２が検知する冷凍室温度T_Ｆが冷凍運転終了温度Ｔ_{Ｆ＿ｏｆｆ}に到達し，且つ，野菜室ダンパ１９が閉鎖されていることから，冷凍運転が終了している。このとき冷蔵室温度センサ４１が検知する冷蔵室温度T_Rが冷蔵運転開始温度T_R＿on以上に達していることから，冷蔵運転開始条件が成立し，冷媒回収運転が行われている。冷媒回収運転では，三方弁５２が状態３（全閉モード）に制御され，圧縮機２４が速度２（１４００min^-1），冷凍用ファン９ｂが速度１（１２００min^-1）で駆動されて，冷凍用冷却器１４ｂ内の冷媒が１．５分間回収される（Δｔ_Ｂ1＝１．５min）。これにより，次の冷蔵運転での冷媒不足による冷却効率低下を抑制することができる。なお，このとき冷凍用ファン９ｂを駆動することで，冷凍用冷却器１４ｂ内の残留冷媒を冷凍室７の冷却に活用するとともに，冷凍室７内の空気による加熱で，冷凍用冷却器１４ｂ内の圧力低下が緩和される。これにより圧縮機２４の吸込冷媒の比体積増加が抑制され，比較的短い時間で多くの冷媒を回収できるようになり，冷却効率を高めることができる。 Freezing compartment temperature T _F of the freezing compartment temperature sensor 42 detects the elapsed time t ₄ reaches the freezing operation completion temperature T _{F_off,} and, since the vegetable compartment damper 19 is closed, the freezing operation is completed . Since this time the refrigerating compartment temperature T _R which is refrigerating chamber temperature sensor 41 detects is reached over the refrigerating operation start temperature T _{R_on,} refrigerating operation start condition is satisfied, the refrigerant recovering operation is performed. In the refrigerant recovery operation, the three-way valve 52 is controlled to the state 3 (fully closed mode), the compressor 24 is driven at speed 2 (1400 min ⁻¹ ), and the refrigeration fan 9 b is driven at speed 1 (1200 min ⁻¹ ). The refrigerant in the cooler 14b is recovered for 1.5 minutes (Δt _B1 = 1.5 min). Thereby, the cooling efficiency fall by the refrigerant | coolant shortage by the following refrigeration operation can be suppressed. At this time, by driving the refrigeration fan 9b, the refrigerant remaining in the refrigeration cooler 14b is used for cooling the freezer compartment 7 and is heated in the freezer compartment 7 by the air in the freezer compartment 7. This reduces the pressure drop. As a result, an increase in the specific volume of the suction refrigerant in the compressor 24 is suppressed, and a large amount of refrigerant can be recovered in a relatively short time, thereby improving the cooling efficiency.

冷凍室７が冷却される運転は，冷凍野菜運転（ｔ２〜ｔ３），冷凍運転（ｔ３〜ｔ４），冷媒回収運転（ｔ４〜ｔ５）であり，これらの運転が行われている間の冷凍用冷却器１４ｂの時間平均温度は約−２４℃となるように，冷凍用ファン９ｂ及び圧縮機２４が制御されている。また，冷蔵用ファン９aが駆動状態となっている冷凍運転と冷蔵用冷却器除霜運転が行われている間の冷蔵室吐出空気温度の時間平均値は，-１.５℃であり，冷凍室維持温度Ｔ_{Ｆ_ｋｅｅｐ}（４℃）と冷蔵室維持温度Ｔ_{Ｒ_keep}（−２０℃）の算術平均値（-8℃）より高い温度となっている。 The operation in which the freezer compartment 7 is cooled includes the frozen vegetable operation (t2 to t3), the freezing operation (t3 to t4), and the refrigerant recovery operation (t4 to t5). The refrigeration fan 9b and the compressor 24 are controlled so that the time average temperature of the cooler 14b is about -24 ° C. Further, the time average value of the discharge temperature of the refrigerating room during the refrigerating operation in which the refrigerating fan 9a is driven and the refrigerating cooler defrosting operation is −1.5 ° C., chamber maintained temperature _{T F_keep} (4 ℃) and the refrigerating compartment maintained temperature _T arithmetic mean of _{R_keep} (-20 ℃) has a temperature higher than (-8 ° C.).

冷媒回収運転が終了した経過時間ｔ₅より再び，冷蔵運転が開始され，以後周期的に上述の運転が繰り返され，冷蔵室２は約４℃，冷凍室７は約-２０℃，野菜室は約７℃に維持される。 The refrigeration operation is started again from the elapsed time t ₅ when the refrigerant recovery operation is completed, and the above operation is repeated periodically thereafter. The refrigeration room 2 is about 4 ° C., the freezing room 7 is about −20 ° C., and the vegetable room is Maintained at about 7 ° C.

ここで，野菜室６は水分が多く含まれる野菜や果物が基本的に貯蔵されるので，野菜室６内の相対湿度は高い状態にある。しかし，本実施例では，冷蔵室２は独立の風路により専用の冷蔵用冷却器１４ａで冷却し，野菜室６は別の風路により別の冷凍用冷却器１４ｂで冷却するので，野菜室６内の空気が冷蔵室２の風路に送風されないようになっている。したがって，野菜室２内の多湿の空気が冷蔵室冷却器１４ａに到達せず、冷蔵室冷却器１４ａへの霜の付着が抑制され、冷蔵室２の冷却性能の低下を防ぐことが可能である。 Here, since the vegetable room 6 basically stores vegetables and fruits containing a lot of water, the relative humidity in the vegetable room 6 is high. However, in this embodiment, the refrigerator compartment 2 is cooled by a dedicated refrigerator 14a by an independent air passage, and the vegetable compartment 6 is cooled by another refrigerator 14b by another air passage. The air in 6 is not sent to the air path of the refrigerator compartment 2. Therefore, the humid air in the vegetable compartment 2 does not reach the refrigerating room cooler 14a, frost adhesion to the refrigerating room cooler 14a is suppressed, and it is possible to prevent the cooling performance of the refrigerating room 2 from deteriorating. .

なお、本発明は上記に示した実施例に限定されるものではなく、様々な変形例が含まれる。例えば、上記に示した実施例は本発明を分かりやすく説明するために詳細に説明したものであり、必ずしも説明した全ての構成を備えるものに限定されるものではない。また、ある実施例の構成の一部を他の実施例の構成に置き換えることが可能であり、また、ある実施例の構成に他の実施例の構成を加えることも可能である。 In addition, this invention is not limited to the Example shown above, Various modifications are included. For example, the embodiments described above have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment.

１冷蔵庫
２冷蔵室（第一冷蔵温度帯室）
２ａ，２ｂ冷蔵室扉
３製氷室
４上段冷凍室
５下段冷凍室冷凍室
３ａ，４ａ，５ａ冷凍室扉
６野菜室（第二冷蔵温度帯室）
６ａ野菜室扉
７冷凍室（３，４，５の総称）
８ａ冷蔵用冷却器室（第一冷却器収納室）
８ｂ冷凍用冷却器室（第二冷却器収納室）
９ａ冷蔵用ファン（第一送風機）
９ｂ冷凍用ファン（第二送風機）
１０断熱箱体
１０ａ外箱
１０ｂ内箱
１１冷蔵室送風路
１１ａ冷蔵室吐出口
１２冷凍室送風路
１２ａ冷凍室吐出口
１３野菜室送風路
１３ａ野菜室吐出口
１４ａ冷蔵用冷却器（第一冷却器）
１４ｂ冷凍用冷却器（第二冷却器）
１５ａ，１５ｂ１５ｃ冷蔵室戻り風路
１６ヒンジカバー
１７冷凍室戻り口
１８野菜室戻り風路
１８ａ野菜室戻り口
１９野菜室ダンパ
２１ラジアントヒータ
２２ａ，２２ｂ排水口
２３ａ，２３ｂ樋
２４圧縮機
２５風路
２６庫外ファン
２７ａ冷蔵用排水管
２７ｂ冷凍用排水管
２８，２９，３０断熱仕切壁
３１制御基板
３２蒸発皿
３５チルドルーム
３９機械室
４０ａ冷蔵用冷却器温度センサ
４０ｂ冷凍用冷却器温度センサ
４１冷蔵室温度センサ
４２冷凍室温度センサ
４３野菜室温度センサ
５０ａ，５０ｂ庫外放熱器（放熱手段）
５０ｃ結露抑制配管（放熱手段）
５１ドライヤ
５２三方弁（冷媒制御手段）
５３ａ冷蔵用キャピラリチューブ（減圧手段）
５３ｂ冷凍用キャピラリチューブ（減圧手段）
５４a 冷蔵用気液分離器
５４ｂ冷凍用気液分離器
５５ａ，５５ｂ熱交換部
５６逆止弁
９１脱臭部材
９５a，９５ｂ冷蔵室パッキン（第一シール部材）
９６a，９６ｂ，９６ｃ冷凍室パッキン（第二シール部材）
９７野菜室パッキン（第三シール部材）
１０１樋部ヒータ
１０２排水管上部ヒータ
１０３排水管下部ヒータ 1 Refrigerator 2 Refrigerated room (first refrigerated temperature room)
2a, 2b Refrigeration room door 3 Ice making room 4 Upper freezing room 5 Lower freezing room Freezing room 3a, 4a, 5a Freezing room door 6 Vegetable room (second refrigeration temperature zone room)
6a Vegetable room door 7 Freezer room (generic name for 3, 4 and 5)
8a Cooler room for refrigeration (first cooler storage room)
8b Refrigeration cooler room (second cooler storage room)
9a Refrigeration fan (first blower)
9b Refrigeration fan (second blower)
DESCRIPTION OF SYMBOLS 10 Heat insulation box 10a Outer box 10b Inner box 11 Refrigeration room ventilation path 11a Refrigeration room discharge port 12 Freezer room ventilation path 12a Freezer room discharge port 13 Vegetable room ventilation path 13a Vegetable room discharge port 14a Refrigeration cooler (first cooler) )
14b Refrigeration cooler (second cooler)
15a, 15b 15c Refrigeration room return air passage 16 Hinge cover 17 Freezer compartment return port 18 Vegetable room return air passage 18a Vegetable room return port 19 Vegetable room damper 21 Radiant heaters 22a, 22b Drainage ports 23a, 23b 樋 24 Compressor 25 Air passage 26 Outside fan 27a Refrigeration drain pipe 27b Refrigeration drain pipe 28, 29, 30 Insulating partition wall 31 Control board 32 Evaporating dish 35 Chilled room 39 Machine room 40a Refrigeration cooler temperature sensor 40b Refrigeration cooler temperature sensor 41 Refrigeration Room temperature sensor 42 Freezer room temperature sensor 43 Vegetable room temperature sensors 50a, 50b External radiator (heat radiation means)
50c Condensation suppression piping (heat dissipation means)
51 Dryer 52 Three-way valve (refrigerant control means)
53a Capillary tube for refrigeration (pressure reduction means)
53b Capillary tube for freezing (pressure reduction means)
54a Refrigeration gas / liquid separator 54b Refrigeration gas / liquid separator 55a, 55b Heat exchange unit 56 Check valve 91 Deodorizing members 95a, 95b Refrigeration chamber packing (first seal member)
96a, 96b, 96c Freezer compartment packing (second seal member)
97 Vegetable room packing (third seal member)
101 Head heater 102 Drain pipe upper heater 103 Drain pipe lower heater

Claims

第一冷蔵温度帯室，第二冷蔵温度帯室，冷凍温度帯室を備え，
前記第一冷蔵温度帯室の背部に設けられた第一冷却器と，前記第一冷却器の冷気を前記第一冷蔵温度帯室に送風する第一送風機と，前記第一冷却器から前記第一冷蔵温度帯室を流れて前記第一冷却器に戻る第一風路と，
前記冷凍温度帯室または前記第二冷蔵温度帯室の背部に設けられた第二冷却器と，前記第二冷却器の冷気を前記冷凍温度帯室または第二冷蔵温度帯室に送風する第二送風機と，前記第二冷却器から前記冷凍温度帯室または前記第二冷蔵温度帯室を流れて前記第二冷却器に戻る第二風路と，を備えた冷蔵庫において，
前記第一風路の吐出口は，前記第一冷蔵温度帯室の前面には設けず，前記第一冷却器からの主流冷気が前記第一冷蔵温度帯室内の壁面に向かうことを特徴とする冷蔵庫。 The first refrigeration temperature zone room, the second refrigeration temperature zone room, the freezing temperature zone room,
A first cooler provided at the back of the first refrigerated temperature zone; a first blower for blowing cool air from the first chiller to the first refrigerated temperature zone; and A first air path that flows through the refrigerated temperature zone and returns to the first cooler;
A second cooler provided at the back of the refrigeration temperature zone chamber or the second refrigeration temperature zone chamber, and a second air for blowing the cool air of the second cooler to the refrigeration temperature zone chamber or the second refrigeration temperature zone chamber In a refrigerator comprising: a blower; and a second air path that flows from the second cooler to the refrigeration temperature zone chamber or the second refrigeration temperature zone chamber and returns to the second cooler.
The discharge port of the first air passage is not provided in front of the first refrigeration temperature zone chamber, and the mainstream cold air from the first cooler is directed to the wall surface in the first refrigeration temperature zone chamber. refrigerator.

請求項１記載の冷蔵庫において，前記第一送風機の駆動時間が前記第二送風機の駆動時間よりも長いことを特徴とする冷蔵庫。 The refrigerator according to claim 1, wherein the driving time of the first blower is longer than the driving time of the second blower.

請求項１記載の冷蔵庫における冷却運転時において，前記第一冷却器の温度が前記第二冷却器の温度よりも高いことを特徴とする冷蔵庫。 The refrigerator according to claim 1, wherein the temperature of the first cooler is higher than the temperature of the second cooler during the cooling operation in the refrigerator according to claim 1.

請求項１記載の冷蔵庫において，前記第一風路の吐出口は、上方を開口したものであり、前記第一冷却器からの主流冷気が前記第一冷蔵温度帯室の天面に向かうことを特徴とする冷蔵庫。 2. The refrigerator according to claim 1, wherein the discharge port of the first air passage opens upward, and mainstream cold air from the first cooler is directed toward the top surface of the first refrigeration temperature zone. Features a refrigerator.