JPH0268214A - Refrigerator for vehicle - Google Patents
Refrigerator for vehicleInfo
- Publication number
- JPH0268214A JPH0268214A JP63219581A JP21958188A JPH0268214A JP H0268214 A JPH0268214 A JP H0268214A JP 63219581 A JP63219581 A JP 63219581A JP 21958188 A JP21958188 A JP 21958188A JP H0268214 A JPH0268214 A JP H0268214A
- Authority
- JP
- Japan
- Prior art keywords
- refrigerator
- cold storage
- cooling
- evaporator
- fins
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000008020 evaporation Effects 0.000 claims abstract description 27
- 238000001704 evaporation Methods 0.000 claims abstract description 27
- 238000005057 refrigeration Methods 0.000 claims description 6
- 238000001816 cooling Methods 0.000 abstract description 31
- 230000000694 effects Effects 0.000 abstract description 9
- 230000008014 freezing Effects 0.000 abstract description 5
- 238000007710 freezing Methods 0.000 abstract description 5
- 239000002826 coolant Substances 0.000 abstract 1
- 239000003507 refrigerant Substances 0.000 description 15
- 238000010586 diagram Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 239000011232 storage material Substances 0.000 description 2
- 230000000052 comparative effect Effects 0.000 description 1
- 239000000284 extract Substances 0.000 description 1
- 230000004927 fusion Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000155 melt Substances 0.000 description 1
- 230000008018 melting Effects 0.000 description 1
- 238000002844 melting Methods 0.000 description 1
- 239000003595 mist Substances 0.000 description 1
- 239000011347 resin Substances 0.000 description 1
- 229920005989 resin Polymers 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
- 230000002195 synergetic effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/00492—Heating, cooling or ventilating [HVAC] devices comprising regenerative heating or cooling means, e.g. heat accumulators
- B60H1/005—Regenerative cooling means, e.g. cold accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/24—Storage receiver heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D16/00—Devices using a combination of a cooling mode associated with refrigerating machinery with a cooling mode not associated with refrigerating machinery
Landscapes
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、車両用冷凍機に係り、詳しくは車両駐車時に
於いても庫内を保冷できる蓄冷式の車両用冷凍機に関す
るものである。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a vehicular refrigerator, and more particularly to a regenerator type vehicular refrigerator that can keep the inside of the refrigerator cool even when the vehicle is parked.
蓄冷式の車両用冷凍機として、例えば実開昭56−49
413号公報に開示されているように、冷凍機の冷蔵庫
内に設置された蒸発器に対して蓄冷板を直列に追加配設
し、車両の走行時は、冷凍機の作動によって庫内を蒸発
器で冷却すると共に蓄冷板を冷却凍結させ、一方、冷凍
機の作動が停止する車両の駐車時は、蓄冷板の融解潜熱
によって庫内を冷却し保冷するものが知られている。As a cold storage type vehicle refrigerator, for example,
As disclosed in Publication No. 413, a cold storage plate is additionally arranged in series with the evaporator installed in the refrigerator of the refrigerator, and when the vehicle is running, the inside of the refrigerator is evaporated by the operation of the refrigerator. There is a known system that cools the inside of the refrigerator and cools the refrigerator using the latent heat of fusion of the cold storage plate when the vehicle is parked when the refrigerator stops operating.
しかしながら、上記構成のものに於いては、蒸発器に対
して蓄冷板を単に直列に追加配設したものであるため、
既設の冷凍機に容易に設置できる利点はあるが、蓄冷板
を冷却する冷媒は、蒸発器で既に蒸発の完了したもので
あるので、蓄冷剤を凍結させる蓄冷能力が小さく蓄冷完
了に長時間を要す。また、単なる平板で構成された従来
の蓄冷板では、庫内空気との熱交換効率が悪く、十分な
冷却性能を発揮するためには蓄冷板の伝熱面積を大きく
する必要があるが、それに伴い装置の大型化を来たすの
で搭載性が問題となる。However, in the above configuration, a cold storage plate is simply added in series with the evaporator, so
Although it has the advantage of being easily installed in an existing refrigerator, the refrigerant that cools the cold storage plate has already been evaporated in the evaporator, so the cold storage capacity to freeze the cold storage agent is small and it takes a long time to complete cold storage. It takes. In addition, conventional cold storage plates made of simply flat plates have poor heat exchange efficiency with the air inside the refrigerator, and in order to achieve sufficient cooling performance, it is necessary to increase the heat transfer area of the cold storage plates. Since this results in an increase in the size of the device, mountability becomes a problem.
本発明は、上記の問題に鑑みてなされたもので、装置の
大型化を伴わないで而も冷凍能力の高い蓄冷式の車両用
冷凍機を提供することを目的とするものである。The present invention has been made in view of the above-mentioned problems, and it is an object of the present invention to provide a regenerator type vehicle refrigerator that has a high refrigerating capacity without increasing the size of the device.
本発明は、上記の目的を達成するために、圧縮機、凝縮
器、減圧装置、蒸発器を順次接続して冷凍サイクルを構
成する車両用冷凍機に於いて、
車両の冷蔵庫内に設置され庫内を冷却する上記蒸発器の
蒸発用チューブと、
この蒸発用チューブに隙間をあけて熱的に接触させて配
された蓄冷パックと、
この蓄冷パックの上記隙間にあって、上記蒸発用チュー
ブに熱的に接触させて配されたフィンと、を備える構成
とするものである。In order to achieve the above-mentioned object, the present invention provides a vehicular refrigeration machine in which a compressor, a condenser, a pressure reducing device, and an evaporator are sequentially connected to form a refrigeration cycle. An evaporation tube of the evaporator that cools the inside of the evaporator, a cold storage pack placed in thermal contact with a gap between the evaporation tubes, and a cold storage pack that is located in the gap between the cold storage packs and connected to the evaporation tubes. The fins are arranged in thermal contact with each other.
上記の手段によれば、庫内を冷却する蒸発器の蒸発用チ
ューブに対して、蓄冷パックとフィンとが熱的に接触さ
せて交互に配設されているので、冷凍機の作動時は冷媒
の蒸発による吸熱作用のため蓄冷パックは冷却されて凍
結し、同時にフィンを介して庫内の空気は熱交換されて
庫内は冷却される。According to the above means, the cold storage pack and the fins are arranged alternately in thermal contact with the evaporation tube of the evaporator that cools the inside of the refrigerator, so when the refrigerator is operating, the refrigerant is Due to the heat absorption effect caused by evaporation, the cold storage pack is cooled and frozen, and at the same time, the air inside the refrigerator is heat-exchanged through the fins, cooling the inside of the refrigerator.
一方、冷凍機の作動停止時は、凍結した蓄冷パックの融
解による吸熱作用のため、庫内は引続き冷却される。On the other hand, when the refrigerator stops operating, the interior of the refrigerator continues to be cooled due to the heat absorption effect caused by the melting of the frozen cold storage pack.
以下、本発明を図に示す実施例について説明する。 DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, embodiments of the present invention shown in the drawings will be described.
第1図は、本発明の車両用冷凍機の一実施例に示す構成
図で、図に於いて、1は冷媒の圧縮と吐出を行う圧縮機
で、車両のエンジン(図示せず)の駆動力を電磁クラッ
チ(図示せず)を介して受けることにより作動するよう
になっている。2は圧縮機lより吐出される高温高圧の
ガス冷媒を層線液化する送風ファン2aを有する凝縮器
、3は凝縮器2で凝縮された冷媒を受けて液冷媒のみを
導出するレシーバ、4はレシーバ3で導出された液冷媒
を低温低圧の霧状冷媒に減圧膨張させる膨張弁である。FIG. 1 is a block diagram showing an embodiment of a vehicle refrigerator according to the present invention. It operates by receiving force via an electromagnetic clutch (not shown). 2 is a condenser having a blower fan 2a that liquefies the high temperature and high pressure gas refrigerant discharged from the compressor 1; 3 is a receiver that receives the refrigerant condensed in the condenser 2 and extracts only liquid refrigerant; 4 is a This is an expansion valve that depressurizes and expands the liquid refrigerant drawn out by the receiver 3 into a low-temperature, low-pressure atomized refrigerant.
この膨張弁4は、冷却ユニット10の蒸発機5の出口側
配管に取付けられた感温筒4aからの温度信号に応じて
、絞り量を可変する温度作動式の自動膨張弁よりなって
いて、上記の圧縮機l、凝縮器2.レシーバ3.膨張弁
4.蒸発器5の順に接続されて冷凍サイクルが構成され
、冷媒は図の矢印の方向に流れて循環する。The expansion valve 4 is a temperature-operated automatic expansion valve that varies the amount of throttling in response to a temperature signal from a temperature sensing cylinder 4a attached to the outlet side piping of the evaporator 5 of the cooling unit 10. The above compressor 1, condenser 2. Receiver 3. Expansion valve 4. The evaporators 5 are connected in this order to form a refrigeration cycle, and the refrigerant flows and circulates in the direction of the arrow in the figure.
第2図(a)は、上記の冷却ユニット10の構成を示す
もので、図に於いて5aはU字型に蛇行曲折したパイプ
よりなる前記蒸発器5を構成する蒸発用チューブで、こ
の蒸発用チューブ5aに対して例えば−5°Cで凍結す
る蓄冷剤が樹脂ケース等でバックされて作られた蓄冷パ
ック6が隙間をあけて熱的に接触させて配され、蒸発用
チューブ5aに設けられたこの隙間には多数のフィン7
が熱的に接触させて配され、冷却ユニットIOが構成さ
れている。FIG. 2(a) shows the configuration of the above cooling unit 10. In the figure, 5a is an evaporation tube constituting the evaporator 5, which is a U-shaped meandering pipe. A cold storage pack 6 made by backing a cold storage agent that freezes at, for example, -5°C with a resin case or the like is placed in thermal contact with the evaporation tube 5a with a gap, and is installed in the evaporation tube 5a. There are many fins 7 in this gap.
are arranged in thermal contact to form a cooling unit IO.
上記の冷却ユニット10のボデー11への取付けは、ボ
デー11の壁に接するブラケット21と、これと同形状
のブラケット22を用いて第2図(b)に示すように2
個の蓄冷パック6を蒸発用チューブ5aに挾む形で取付
け、ブラケット21と22の上方と下方にボルト23を
挿通して、ボデー11の壁に埋込み固定されたナツトに
螺合締付けて固定される。なお、冷却ユニント10の下
部には蓄冷パック6やフィン7に付着した霜が溶けた場
合に、これを庫外に排出するためのドレーンパン9が配
設されている。The cooling unit 10 described above is attached to the body 11 using a bracket 21 in contact with the wall of the body 11 and a bracket 22 having the same shape as shown in FIG. 2(b).
The cold storage packs 6 are attached to the evaporation tube 5a in a sandwiched manner, and the bolts 23 are inserted above and below the brackets 21 and 22, and then screwed and tightened to the nuts embedded and fixed in the wall of the body 11. Ru. Note that a drain pan 9 is provided at the bottom of the cooling unit 10 to discharge frost adhering to the cold storage pack 6 and the fins 7 to the outside of the refrigerator when it melts.
第3図(a)は、上記の冷却ユニッ1−10を車両に搭
載した場合を示す模式図で、図に於いて圧縮機1は車両
のエンジンに直結駆動されるように搭載され、凝縮器2
はボデー11のフロント上部に搭載され、冷却ユニット
10はボデー11の中に設けられた冷蔵庫8内に設置さ
れる。なお、冷却ユニット10は、第3図(b)に示す
ように冷蔵庫8の中にあってガード12により固定され
、積荷から保護されている。FIG. 3(a) is a schematic diagram showing the case where the above-mentioned cooling unit 1-10 is mounted on a vehicle. 2
is mounted on the front upper part of the body 11, and the cooling unit 10 is installed in the refrigerator 8 provided inside the body 11. Note that, as shown in FIG. 3(b), the cooling unit 10 is located inside the refrigerator 8 and is fixed by a guard 12 to be protected from cargo.
次に、上記の実施例についてその作動を説明する。Next, the operation of the above embodiment will be explained.
第1図に於いて、車両のエンジン(図示せず)によって
回転駆動される圧縮機1の作動により、圧縮された冷媒
は凝縮器2で凝縮され、レシーバ3で気液に分離されて
液冷媒が膨張弁4に送られ、膨張弁4で減圧膨張して霧
状冷媒となり、この霧状冷媒は冷蔵庫内に設置された冷
却ユニット10の蒸発器5で蒸発し、蒸発の際に周囲よ
り熱が奪われるので庫内が冷却される。そのため、蒸発
器5の蒸発用チューブ5aに熱的に接触させて配された
蓄冷バック6は、凍結点(例えば−5°C)に冷却され
て凍結され、一方、蒸発用チューブ5aに熱的に接触さ
せて配されたフィン7によって、庫内の空気は直接冷却
される。In FIG. 1, compressed refrigerant is condensed in a condenser 2 by the operation of a compressor 1 which is rotationally driven by a vehicle engine (not shown), and is separated into gas and liquid in a receiver 3 to form liquid refrigerant. is sent to the expansion valve 4, where it is decompressed and expanded to become a mist refrigerant, and this atomized refrigerant is evaporated in the evaporator 5 of the cooling unit 10 installed in the refrigerator. is taken away, so the inside of the refrigerator is cooled. Therefore, the cold storage bag 6 placed in thermal contact with the evaporation tube 5a of the evaporator 5 is cooled to the freezing point (for example, -5°C) and frozen, while the evaporation tube 5a is The air inside the refrigerator is directly cooled by the fins 7 placed in contact with the fins 7 .
第4図は、本発明の蒸発用チューブ5aに配した蓄冷パ
ック6とフィン7の表面温度、及び本発明(蒸発用チュ
ーブ5aに蓄冷パック6とフィン7を交互に配した冷却
ユニット10によるもの)の庫内温度、さらに比較品(
蒸発用チューブ5aに蓄冷パック6のみ配した冷却ユニ
ットによるもの)の庫内温度について、外気温度及び庫
内初期温度が35°Cからのクールダウン特性を示した
ものである。なお、蓄冷パック6の凍結点は一5℃のも
のを用い、本発明と比較品との蒸発用チューブ5aは同
一のものを用いて行った。FIG. 4 shows the surface temperatures of the cold storage packs 6 and fins 7 arranged on the evaporation tube 5a of the present invention, and the cooling unit 10 of the present invention (cool storage packs 6 and fins 7 arranged alternately on the evaporation tube 5a). ) and the internal temperature of the comparative product (
The figure shows the cool-down characteristics for the internal temperature of a cooling unit (based on a cooling unit in which only the cold storage pack 6 is arranged in the evaporation tube 5a) from an outside temperature and an initial internal temperature of 35°C. The cold storage pack 6 with a freezing point of -5° C. was used, and the evaporation tube 5a of the present invention and the comparison product were the same.
図に示すように、フィン温度は運転開始から10分後に
は一20°C付近まで下がり、その後は僅かながら低く
なって行くのに対し、蓄冷バック温度は、運転開始から
約2時間後に凍結点の一5°Cに下がり、その後は全体
の凍結が完了するまで約2時間に渡り一5°Cを継続し
てから過冷却点に達する。本発明の庫内温度は、−20
’Cのフィンによる庫内空気との熱交換で冷却されて行
くが、庫内空気の熱容量は蓄冷パンクロの熱容量に比べ
てはるかに小さいため、クールダウンの初期は蓄冷パッ
ク6よりも速く下がり、運転開始から約30分後には冷
蔵管理温度の5°Cに達し、その後はボデー11の壁を
通して伝達される熱負荷とバランスしなから0゛C付近
まで徐々に下がって行く。As shown in the figure, the fin temperature drops to around -20°C 10 minutes after the start of operation, and then decreases slightly after that, while the temperature in the cold storage bag reaches the freezing point about 2 hours after the start of operation. After that, the temperature is maintained at 15°C for about 2 hours until the entire freezing is completed, and then the supercooling point is reached. The internal temperature of the present invention is -20
It is cooled by heat exchange with the air inside the refrigerator by the fins of 'C, but since the heat capacity of the air inside the refrigerator is much smaller than that of the cold storage panchromator, it decreases faster than the cold storage pack 6 at the beginning of the cooldown. Approximately 30 minutes after the start of operation, the temperature reaches the refrigeration control temperature of 5°C, and then gradually decreases to around 0°C, out of balance with the heat load transmitted through the wall of the body 11.
これに対し、比較品の庫内温度は、運転開始から約2時
間後で一5°Cに下がる蓄冷パック6による庫内空気と
の熱交換で冷却されて行くため、冷蔵管理温度5 ”C
への到達時間は約2時間を要し、本発明の庫内温度のク
ールダウン性能に比べて大[11に悪い。本発明の庫内
温度のクールダウン性能が良い理由は、蒸発用チューブ
5aの冷媒の蒸発温度と略同レベルの低い温度で応動す
るフィン7の冷却作用によるもので、フィン7の冷却作
用による効果は、冷凍機作動時のクールダウン性能の向
上だけでなく、冷凍機停止時の蓄冷パック6のみによる
冷却状態時に於いても相乗作用により冷却性能の向上に
寄与している。On the other hand, the internal temperature of the comparison product drops to 15°C approximately 2 hours after the start of operation, and is cooled by heat exchange with the internal air by the cold storage pack 6, so the refrigeration control temperature is 5''C.
It takes about 2 hours to reach this temperature, which is significantly worse than the cool-down performance of the present invention. The reason why the cool-down performance of the refrigerator interior temperature of the present invention is good is due to the cooling effect of the fins 7, which respond at a low temperature that is approximately the same level as the evaporation temperature of the refrigerant in the evaporation tube 5a. This not only improves the cool-down performance when the refrigerator is in operation, but also contributes to the improvement of the cooling performance through a synergistic effect even when the refrigerator is in a cooling state using only the cold storage pack 6 when the refrigerator is stopped.
次に、本実施例では、フィン7と庫内空気の熱交換は、
自然対流による自然冷却によったが、冷却性能を向上す
るため、庫内に送風ファンを設置してフィン7と蓄冷パ
ック6の表面に送風して強制対流による強制冷却を行っ
ても良い。Next, in this embodiment, the heat exchange between the fins 7 and the air inside the refrigerator is as follows.
Although natural cooling is performed by natural convection, in order to improve the cooling performance, a blower fan may be installed in the refrigerator to blow air onto the surfaces of the fins 7 and the cold storage pack 6 to perform forced cooling by forced convection.
なお、本実施例では冷却ユニット10をボデー11の片
方の側壁に設置したが、必要に応じて両方の側壁に設置
しても良く、或いは前壁に設置しても良い。In this embodiment, the cooling unit 10 is installed on one side wall of the body 11, but it may be installed on both side walls, or on the front wall, if necessary.
また、本実施例では、減圧装置4として温度作動式の自
動膨張弁を用いたが、通常の定圧膨張弁或いはキャピラ
リーでも良く、冷媒を減圧し膨張させるものならば良い
。Further, in this embodiment, a temperature-operated automatic expansion valve is used as the pressure reducing device 4, but a normal constant pressure expansion valve or a capillary may be used as long as it reduces the pressure and expands the refrigerant.
本発明は、以上説明したように構成されているので、以
下に記載するような効果を奏する。Since the present invention is configured as described above, it produces the effects described below.
(イ)冷媒の蒸発温度と略同じ温度で応動するフィンの
冷却作用により庫内空気は直列冷却されるので、冷凍能
力が高く且つ冷却が速い。(a) Since the air inside the refrigerator is cooled in series by the cooling action of the fins that respond at approximately the same temperature as the evaporation temperature of the refrigerant, the refrigerating capacity is high and cooling is fast.
(ロ)フィンの冷却作用により蓄冷パックの保冷能力が
大きいので、長時間の停車中に於いても、従来のように
冷凍機を特別に作動させる必要はない。(b) Since the cooling capacity of the cold storage pack is large due to the cooling effect of the fins, there is no need to operate the refrigerator specially like in the past even when the vehicle is stopped for a long time.
(ハ)蒸発用チューブに蓄冷パックとフィンとを交互に
配する構造であるので、装置はコンパクトにまとめられ
る。(c) Since the structure is such that cold storage packs and fins are arranged alternately on the evaporation tube, the device can be made compact.
第1図は本発明の車両用冷凍機の一実施例を示す構成図
、第2図(a)は同冷凍機の冷却ユニットの斜視図、第
2図(ロ)は第2図(a)の要部の取付を示す斜視図、
第3図(a)は同冷凍機の冷却ユニットの車両搭載を示
す側面の模式図、第3図(b)は同断面の模式図、第4
図は作動説明のためのクールダウン特性図である。
1・・・圧縮機、2・・・凝縮器、4・・・膨張弁(減
圧装置)、5・・・蒸発器、5a・・・蒸発用チューブ
、6・・・蓄冷パック、7・・・フィン、8・・・冷蔵
庫。FIG. 1 is a configuration diagram showing an embodiment of a vehicle refrigerator of the present invention, FIG. 2(a) is a perspective view of a cooling unit of the refrigerator, and FIG. A perspective view showing the installation of the main parts of the
Fig. 3(a) is a schematic side view showing the cooling unit of the refrigerator mounted on a vehicle, Fig. 3(b) is a schematic cross-sectional view of the same, and Fig. 4
The figure is a cool-down characteristic diagram for explaining the operation. DESCRIPTION OF SYMBOLS 1... Compressor, 2... Condenser, 4... Expansion valve (pressure reducing device), 5... Evaporator, 5a... Evaporation tube, 6... Cold storage pack, 7...・Fin, 8...refrigerator.
Claims (1)
サイクルを構成する車両用冷凍機に於いて、 車両の冷蔵庫内に設置され庫内を冷却する上記蒸発器の
蒸発用チューブと、 この蒸発用チューブに隙間をあけて熱的に接触させて配
された蓄冷パックと、 この蓄冷パックの上記隙間にあって、上記蒸発用チュー
ブに熱的に接触させて配されたフィンと、を備えたこと
を特徴とする車両用冷凍機。[Scope of Claims] In a vehicle refrigerator in which a compressor, a condenser, a pressure reducing device, and an evaporator are sequentially connected to form a refrigeration cycle, the evaporator is installed in a refrigerator of a vehicle and cools the inside of the refrigerator. an evaporation tube, a cold storage pack disposed in thermal contact with the evaporation tube with a gap, and a cold storage pack disposed in the gap between the cold storage pack and in thermal contact with the evaporation tube. A vehicular refrigerator characterized by comprising:
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63219581A JPH0268214A (en) | 1988-09-01 | 1988-09-01 | Refrigerator for vehicle |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP63219581A JPH0268214A (en) | 1988-09-01 | 1988-09-01 | Refrigerator for vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
JPH0268214A true JPH0268214A (en) | 1990-03-07 |
Family
ID=16737772
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP63219581A Pending JPH0268214A (en) | 1988-09-01 | 1988-09-01 | Refrigerator for vehicle |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0268214A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0995621A3 (en) * | 1998-10-23 | 2001-03-14 | Denso Corporation | Vehicle air conditioning system |
JP2011051491A (en) * | 2009-09-02 | 2011-03-17 | Denso Corp | Air conditioning device for vehicle |
JP2017172848A (en) * | 2016-03-23 | 2017-09-28 | パナソニックIpマネジメント株式会社 | refrigerator |
-
1988
- 1988-09-01 JP JP63219581A patent/JPH0268214A/en active Pending
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0995621A3 (en) * | 1998-10-23 | 2001-03-14 | Denso Corporation | Vehicle air conditioning system |
US6330909B1 (en) | 1998-10-23 | 2001-12-18 | Denso Corporation | Vehicle air conditioning system |
EP1787838A1 (en) * | 1998-10-23 | 2007-05-23 | Denso Corporation | Vehicle air conditioning system |
JP2011051491A (en) * | 2009-09-02 | 2011-03-17 | Denso Corp | Air conditioning device for vehicle |
US8857201B2 (en) | 2009-09-02 | 2014-10-14 | Denso Corporation | Air-conditioning device for vehicle |
JP2017172848A (en) * | 2016-03-23 | 2017-09-28 | パナソニックIpマネジメント株式会社 | refrigerator |
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