JP4355604B2 - Heat exchange system - Google Patents

Heat exchange system Download PDF

Info

Publication number
JP4355604B2
JP4355604B2 JP2004100266A JP2004100266A JP4355604B2 JP 4355604 B2 JP4355604 B2 JP 4355604B2 JP 2004100266 A JP2004100266 A JP 2004100266A JP 2004100266 A JP2004100266 A JP 2004100266A JP 4355604 B2 JP4355604 B2 JP 4355604B2
Authority
JP
Japan
Prior art keywords
radiator
refrigerant
heat exchange
exchange system
cooling air
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.)
Expired - Fee Related
Application number
JP2004100266A
Other languages
Japanese (ja)
Other versions
JP2005283021A (en
Inventor
隆司 藤田
寅秀 高橋
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Calsonic Kansei Corp
Original Assignee
Calsonic Kansei Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Calsonic Kansei Corp filed Critical Calsonic Kansei Corp
Priority to JP2004100266A priority Critical patent/JP4355604B2/en
Publication of JP2005283021A publication Critical patent/JP2005283021A/en
Application granted granted Critical
Publication of JP4355604B2 publication Critical patent/JP4355604B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0435—Combination of units extending one behind the other
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0073—Gas coolers

Description

本発明は熱交換システムに関し、さらに詳しくは、超臨界下で運転される例えば二酸化炭素を冷媒として用いる冷凍サイクルの放熱器の配置に関するものである。   The present invention relates to a heat exchange system, and more particularly to an arrangement of a radiator for a refrigeration cycle that uses, for example, carbon dioxide as a refrigerant that is operated under supercritical conditions.

従来の空調システムでは、ＨＦＣ１３４ａなどのフロン系冷媒が用いられた冷凍サイクルを利用しているが、オゾン層の破壊や地球の温暖化といった環境問題が懸念されている。このため、脱フロン対策の一つとして、二酸化炭素、エチレン、エタン、酸化窒素などを冷媒として用いる冷凍サイクルが提案されている（例えば、特許文献１参照。）。これら二酸化炭素などを冷媒として用いる冷凍サイクルは、原理的にはフロン系冷媒を用いた従来の冷凍サイクルと同じである。   The conventional air conditioning system uses a refrigeration cycle in which a chlorofluorocarbon refrigerant such as HFC134a is used, but there are concerns about environmental problems such as destruction of the ozone layer and global warming. For this reason, a refrigeration cycle that uses carbon dioxide, ethylene, ethane, nitric oxide, or the like as a refrigerant has been proposed as one of measures against chlorofluorocarbons (see, for example, Patent Document 1). The refrigeration cycle using carbon dioxide or the like as a refrigerant is in principle the same as a conventional refrigeration cycle using a fluorocarbon refrigerant.

従来のフロン系冷媒を用いた冷凍サイクルでは、放熱器内で冷媒が凝縮状態となるため、放熱器内での温度勾配は極めて小さい。   In a conventional refrigeration cycle using a fluorocarbon refrigerant, the refrigerant is in a condensed state in the radiator, so the temperature gradient in the radiator is extremely small.

一方、二酸化炭素を冷媒として用いる冷凍サイクルのように、放熱時に冷媒状態が超臨界下で運転される放熱器では、通過する冷媒はガス体である。また、放熱器の入口では、冷媒が１００℃以上の高温となるが、放熱器に流入した後は、冷却風と急激に熱交換して冷却される特性がある。このように、二酸化炭素を冷媒として用いた冷凍サイクルでは、放熱器において冷媒の入口と出口との間で温度勾配が急峻となる特性がある。このように、この放熱器に別の放熱器を対向するように配置して冷却風を共用することは行われていなかった。
特公平７−１８６０２号公報 On the other hand, in a radiator that operates under supercritical refrigerant conditions during heat dissipation, such as a refrigeration cycle using carbon dioxide as a refrigerant, the refrigerant that passes through is a gas body. In addition, the refrigerant has a high temperature of 100 ° C. or more at the inlet of the radiator, but after flowing into the radiator, there is a characteristic that it is cooled by rapidly exchanging heat with cooling air. Thus, the refrigeration cycle using carbon dioxide as the refrigerant has a characteristic that the temperature gradient is steep between the inlet and the outlet of the refrigerant in the radiator. Thus, it has not been carried out to share cooling air by arranging another radiator to face this radiator.
Japanese Patent Publication No. 7-18602

上述のように、冷媒が超臨界下で運転される空調システムでは、その放熱器内の温度勾配が急峻であるため、その放熱器を通過してくる冷却風の温度も分布が発生するものであった。このため、この冷凍サイクルの放熱器に別の放熱器を対向配置して冷却風を共用させようとした場合に、何れか一方の放熱器において、ともすると吸熱が起きてしまい放熱性能を阻害してしまう可能性があった。   As described above, in an air conditioning system in which a refrigerant is operated under supercritical conditions, the temperature gradient in the radiator is steep, and thus the temperature of the cooling air passing through the radiator also has a distribution. there were. For this reason, when another radiator is placed opposite to the radiator of this refrigeration cycle to share the cooling air, either one of the radiators will absorb heat, impairing the heat radiation performance. There was a possibility.

このような理由から、冷媒が超臨界下で運転される冷凍サイクルの放熱器に他の放熱器を対向させて配置して熱交換を行う熱交換システムはなかった。具体的には、例えば車両のエンジンルームなどにおいて空調システムの放熱器と他の放熱器などとを互いに干渉しない配置としていた。   For these reasons, there has been no heat exchange system for exchanging heat by disposing another radiator to face a radiator of a refrigeration cycle in which the refrigerant is operated under supercritical conditions. Specifically, for example, in an engine room of a vehicle, the radiator of the air conditioning system and other radiators are arranged so as not to interfere with each other.

そこで、本発明の目的は、冷媒が超臨界下で運転される冷凍サイクルの放熱器と、他の放熱体もしくは発熱体とを対向して配置することを可能にして省スペース化を図ることができる熱交換システムを提供することにある。   Accordingly, an object of the present invention is to save space by allowing a radiator of a refrigeration cycle in which a refrigerant is operated under supercriticality and another radiator or a heating element to face each other. It is to provide a heat exchange system that can.

請求項１記載の発明は、冷媒が超臨界下で運転される冷凍サイクルの第１放熱器と、該第１放熱器の冷却風が通過する領域の一部に対向するように他の第２放熱器とを、互いに放熱を維持するように配置させ、前記第１放熱器における冷媒の下流側領域に対向するように、前記第２放熱器を前記第１放熱器よりも冷却風の下流側に配置させたことを特徴としている。 The invention according to claim 1 is the first radiator of the refrigeration cycle in which the refrigerant is operated under supercriticality, and the other second so as to face a part of the region through which the cooling air of the first radiator passes. The radiator is disposed so as to maintain heat radiation, and the second radiator is disposed downstream of the first radiator with respect to the cooling air so as to face the downstream region of the refrigerant in the first radiator. It is characterized by having been arranged in.

請求項２記載の発明は、冷媒が超臨界下で運転される冷凍サイクルの第１放熱器と、該第１放熱器の冷却風が通過する領域の一部に対向するように他の第２放熱器と、を配置させると共に、前記第１放熱器と前記第２放熱器とのうち、互いに対向する領域における内部冷媒の温度が低い方を冷却風の上流側に配置させ、前記第１放熱器における冷媒の下流側領域に対向するように、前記第２放熱器を前記第１放熱器よりも冷却風の下流側に配置させたことを特徴としている。 According to the second aspect of the present invention, the second radiator of the refrigeration cycle in which the refrigerant is operated under supercriticality and the other second so as to face a part of the region through which the cooling air of the first radiator passes. a radiator, dissipate arranged, of the second radiator and the first radiator, is located on the upstream side of the cooling air towards the internal temperature of the coolant is low in the region facing each other, said first radiator The second radiator is arranged on the downstream side of the cooling air from the first radiator so as to face the downstream region of the refrigerant in the cooler.

請求項３記載の発明は、請求項１又は請求項２に記載の発明であって、前記第２放熱器の冷媒の流れ方向が前記下流側領域における冷媒の流れ方向と逆方向であることを特徴としている。 Invention of Claim 3 is invention of Claim 1 or Claim 2, Comprising: The flow direction of the refrigerant | coolant of a said 2nd radiator is a reverse direction to the flow direction of the refrigerant | coolant in the said downstream area | region. It is a feature.

請求項４記載の発明は、請求項１乃至請求項３のいずれか一項に記載された熱交換システムであって、前記第１放熱器は、一対の平行なヘッダと、前記ヘッダ間を結ぶ複数のチューブと、前記チューブ間に配置されたフィンと、を備えてなることを特徴としている。 Invention of Claim 4 is the heat exchange system as described in any one of Claim 1 thru | or 3 , Comprising: A said 1st heat radiator connects a pair of parallel header and the said header. It is characterized by comprising a plurality of tubes and fins arranged between the tubes.

請求項５記載の発明は、請求項４記載の発明であって、前記チューブは、前記ヘッダの長手方向に沿って複数の冷媒パスに区分され、互いに隣接する前記冷媒パス同士は互いに異なる方向に冷媒を案内することを特徴としている。 The invention according to claim 5 is the invention according to claim 4 , wherein the tube is divided into a plurality of refrigerant paths along a longitudinal direction of the header, and the refrigerant paths adjacent to each other are in different directions. It is characterized by guiding the refrigerant.

請求項６記載の発明は、請求項１乃至請求項５のいずれか一項に記載された熱交換システムであって、前記第２放熱器が電熱ヒータであることを特徴としている。 A sixth aspect of the present invention is the heat exchange system according to any one of the first to fifth aspects, wherein the second radiator is an electric heater.

本発明によれば、超臨界下で運転される熱交換システムの第１放熱器の冷却風上流側もしくは下流側に、他の第２放熱器を対向して配置することが可能となり、熱交換システムが収納される空間、特に車両の内部空間における放熱器の設置スペースの有効利用ならびに省スペース化が図れる。   According to the present invention, it is possible to dispose another second radiator on the upstream side or downstream side of the cooling air of the first radiator of the heat exchange system operated under supercriticality, so that heat exchange can be performed. It is possible to effectively use the space for installing the radiator in the space in which the system is stored, particularly in the interior space of the vehicle, and to save space.

以下、本発明の実施の形態に係る熱交換システムをの詳細を図面に基づいて説明する。本実施の形態に係る熱交換システムは、冷媒として二酸化炭素を用いる車両用空調システムを燃料電池自動車に適用した例である。   Hereinafter, details of a heat exchange system according to an embodiment of the present invention will be described with reference to the drawings. The heat exchange system according to the present embodiment is an example in which a vehicle air conditioning system using carbon dioxide as a refrigerant is applied to a fuel cell vehicle.

（第１の実施の形態）
次に、図１〜図５を用いて本発明の第１の実施の形態について説明する。 (First embodiment)
Next, a first embodiment of the present invention will be described with reference to FIGS.

図１は本発明の第１の実施の形態に係る熱交換システムの概略を示す回路図である。図１に示すように、この熱交換システムは、周知の冷凍サイクルと、この冷凍サイクルにおける後述する第１放熱器（車室外放熱器）４に対向配置させた第２放熱器１０とを備えてなる。   FIG. 1 is a circuit diagram showing an outline of a heat exchange system according to a first embodiment of the present invention. As shown in FIG. 1, the heat exchange system includes a known refrigeration cycle and a second radiator 10 disposed to face a first radiator (outside cabin radiator) 4 described later in the refrigeration cycle. Become.

冷凍サイクルは、圧縮機１、室内放熱器２、三方弁３、第１放熱器４、チェック弁５、内部熱交換器６、膨張弁７、エバポレータ８、アキュムレータ９などで大略構成されている。第２放熱器１０は、上記の第１放熱器４の冷却風上流側に対向配置されている。   The refrigeration cycle generally includes a compressor 1, an indoor radiator 2, a three-way valve 3, a first radiator 4, a check valve 5, an internal heat exchanger 6, an expansion valve 7, an evaporator 8, an accumulator 9, and the like. The second radiator 10 is disposed to face the cooling air upstream side of the first radiator 4.

次に、本実施の形態に係る熱交換システムの特徴を図２および図３を用いて説明する。なお、図２は第１放熱器４のみを示す斜視図であり、図３は第１放熱器４と第２放熱器１０とを対向配置させた状態を示す斜視図である。   Next, features of the heat exchange system according to the present embodiment will be described with reference to FIGS. 2 and 3. 2 is a perspective view showing only the first radiator 4, and FIG. 3 is a perspective view showing a state in which the first radiator 4 and the second radiator 10 are arranged to face each other.

図２および図３に示すように、第１放熱器４は、一対の平行なヘッダ１１、１２を連結する複数のチューブ１３が互いに平行をなすように配置されている。これらチューブ１３同士の間隙には、放熱用のフィン１４が介在されている。なお、ヘッダ１１、１２間の複数のチューブ１３が連結された領域は、冷媒パス１７となっている。   As shown in FIGS. 2 and 3, the first radiator 4 is arranged such that a plurality of tubes 13 that connect a pair of parallel headers 11 and 12 are parallel to each other. A heat dissipation fin 14 is interposed in the gap between the tubes 13. A region where a plurality of tubes 13 between the headers 11 and 12 are connected is a refrigerant path 17.

ヘッダ１１、１２は、長手方向の両端部が閉塞されている。ヘッダ１１の一方（図中上側）の端部近傍の外側部には、冷媒入口１５が設けられている。また、ヘッダ１２の他方（図中下側）の端部近傍の外側部には、冷媒出口１６が設けられている。また、ヘッダ１１の一方の端部からこのヘッダ１１の全長の略三分の一の長さ位置には、内部空間を遮断する隔壁１１Ａが形成されている。一方、ヘッダ１２の他方の端部からこのヘッダ１２の全長の略三分の一の長さ位置には、内部空間を遮断する隔壁１２Ａが形成されている。   The headers 11 and 12 are closed at both ends in the longitudinal direction. A refrigerant inlet 15 is provided in the outer portion near one end (upper side in the drawing) of the header 11. In addition, a refrigerant outlet 16 is provided in the outer portion near the other end (lower side in the drawing) of the header 12. In addition, a partition wall 11 </ b> A that blocks the internal space is formed at a position that is approximately one third of the length of the header 11 from one end of the header 11. On the other hand, a partition wall 12 </ b> A that blocks the internal space is formed at a position that is approximately one third of the total length of the header 12 from the other end of the header 12.

なお、図２に示すように、冷媒パス１７は、上流側冷媒パス１７Ａ、中間冷媒パス１７Ｂ、下流側冷媒パス１７Ｃの３つの領域に区画されている。そして、上流側冷媒パス１７Ａは、ヘッダ１１に形成された隔壁１１Ａより一方の端部側（図中上側）に配置されている。中間冷媒パス１７Ｂは、ヘッダ１１に形成された隔壁１１Ａとヘッダ１２に形成された隔壁１２Ａとの間の領域に配置されている。下流側冷媒パス１７Ｃは、ヘッダ１２に形成された隔壁１２Ａより他方の端部側（図中下側）に配置されている。   As shown in FIG. 2, the refrigerant path 17 is divided into three regions: an upstream refrigerant path 17A, an intermediate refrigerant path 17B, and a downstream refrigerant path 17C. The upstream refrigerant path 17A is arranged on one end side (upper side in the drawing) from the partition wall 11A formed in the header 11. The intermediate refrigerant path 17 </ b> B is disposed in a region between the partition wall 11 </ b> A formed in the header 11 and the partition wall 12 </ b> A formed in the header 12. The downstream refrigerant path 17C is disposed on the other end side (lower side in the drawing) from the partition wall 12A formed in the header 12.

このような第１放熱器４においては、冷媒入口１５から上流側冷媒パス１７Ａを経てヘッダ１２に移動し、ヘッダ１２に至った冷媒はヘッダ１２の隔壁１２Ａで規制されるため中間冷媒パス１７Ｂに流れ込む。そして、中間冷媒パス１７Ｂを経てヘッダ１１に移動した冷媒は、ヘッダ１１の隔壁１１Ａでヘッダ１１の一方の端部側へは移動が規制されているため、他方の端部側へ移動して下流側冷媒パス１７Ｃへ流れ込み、ヘッダ１２の冷媒出口１６から出るようになっている。このように、第１放熱器４では、冷媒は上流側冷媒パス１７Ａ、中間冷媒パス１７Ｂ、下流側冷媒パス１７Ｃの３つのパスをジグザグ状に流れるようになっている。   In such a first radiator 4, the refrigerant moves from the refrigerant inlet 15 to the header 12 via the upstream refrigerant path 17 </ b> A, and the refrigerant reaching the header 12 is regulated by the partition wall 12 </ b> A of the header 12. Flows in. The refrigerant that has moved to the header 11 via the intermediate refrigerant path 17B is restricted to move to one end side of the header 11 by the partition wall 11A of the header 11, and therefore moves to the other end side and flows downstream. The refrigerant flows into the side refrigerant path 17 </ b> C and exits from the refrigerant outlet 16 of the header 12. As described above, in the first radiator 4, the refrigerant flows in a zigzag manner through the three paths of the upstream refrigerant path 17A, the intermediate refrigerant path 17B, and the downstream refrigerant path 17C.

ここで、第２放熱器１０の構成、配置位置の説明に先駆けて、本実施の形態の第１放熱器４における冷媒入口１５から冷媒出口１６へ向けた冷媒の温度を測定した結果を示す図４に基づいて説明する。   Here, the figure which shows the result of having measured the temperature of the refrigerant | coolant which went to the refrigerant | coolant inlet 15 from the refrigerant | coolant inlet 15 in the 1st radiator 4 of this Embodiment prior to description of the structure of 2nd heat radiator 10, and an arrangement position. 4 will be described.

図４に示すように、冷媒入口（ガスクーラ入口）１５に入り込む冷媒温度は約１４０℃であるが、上流側冷媒パス１７Ａを通過してヘッダ１２に至るまでに（パス数０〜１の間に）、約５８℃まで低下している。また、ヘッダ１２から中間冷媒パス１７Ｂを通ってヘッダ１１に至るまでの間に（パス数１〜２の間に）、冷媒温度は約５８℃から約４３℃まで低下している。さらに、ヘッダ１１から下流側冷媒パス１７Ｃを通過してヘッダ１２に至るまでの間に（パス数２〜３の間に）、冷媒温度は約４３℃から約３８℃まで低下している。   As shown in FIG. 4, the refrigerant temperature entering the refrigerant inlet (gas cooler inlet) 15 is about 140 ° C., but passes through the upstream refrigerant path 17A and reaches the header 12 (between the number of passes of 0 to 1). ), About 58 ° C. In addition, the refrigerant temperature decreases from about 58 ° C. to about 43 ° C. during the period from the header 12 through the intermediate refrigerant path 17B to the header 11 (between the number of passes 1 to 2). Further, the refrigerant temperature is lowered from about 43 ° C. to about 38 ° C. from the header 11 through the downstream refrigerant path 17C to the header 12 (between two and three passes).

図４から判るように、冷媒温度は冷媒入口１５から入って上流側冷媒パス１７Ａを通過することにより、急激に冷却される。これに比較して、中間冷媒パス１７Ｂと下流側冷媒パス１７Ｃとを通過したときの冷媒の温度降下は小さくなる。   As can be seen from FIG. 4, the refrigerant temperature is rapidly cooled by entering from the refrigerant inlet 15 and passing through the upstream refrigerant path 17A. Compared to this, the temperature drop of the refrigerant when passing through the intermediate refrigerant path 17B and the downstream refrigerant path 17C becomes smaller.

次に、第２放熱器１０の構成を説明する。図３に示すように、第２放熱器１０は、第１放熱器４の幅寸法と同程度の幅寸法に設定されている。   Next, the configuration of the second radiator 10 will be described. As shown in FIG. 3, the second radiator 10 is set to a width dimension that is approximately the same as the width dimension of the first radiator 4.

第２放熱器１０は、互いに平行な一対のヘッダ１８、１９と、これらヘッダ１８、１９を連結する互いに平行な複数のチューブ２０と、これらチューブ２０同士の間に介在されたフィン２１とを備えてなる。   The second radiator 10 includes a pair of headers 18 and 19 that are parallel to each other, a plurality of parallel tubes 20 that connect the headers 18 and 19, and fins 21 that are interposed between the tubes 20. It becomes.

ヘッダ１８、１９は、第１放熱器４のヘッダ１１、１２の長さの三分の一の長さに設定されている。また、チューブ２０の長さは、第１放熱器４のチューブ１３とほぼ同じ長さに設定されている。そして、ヘッダ１８、１９の外側部のほぼ中央に冷媒入口１８Ａ、１９Ａが設けられている。   The headers 18 and 19 are set to one third of the length of the headers 11 and 12 of the first radiator 4. The length of the tube 20 is set to be substantially the same as the length of the tube 13 of the first radiator 4. Then, refrigerant inlets 18A and 19A are provided in the approximate center of the outer portions of the headers 18 and 19, respectively.

本実施の形態では、このような構成の第２放熱器１０は、例えば燃料電池自動車用の放熱器であり、動力系を冷却する放熱器であるが、この他に燃料電池系を冷却する放熱器を適用することもできる。   In the present embodiment, the second radiator 10 having such a configuration is a radiator for a fuel cell vehicle, for example, and is a radiator that cools the power system. In addition, the heat radiator that cools the fuel cell system is used. A vessel can also be applied.

本実施の形態では、上述した第１放熱器４の現象を踏まえ、図３に示すように、第２放熱器１０を、第１放熱器４の上流側冷媒パス１７Ａと対向するように、冷却風上流側に配置している。そして、第２放熱器１０内の冷媒の温度は、第１放熱器４の上流側冷媒パス１７Ａ内の冷媒の温度以下に設定している。   In the present embodiment, based on the phenomenon of the first radiator 4 described above, the second radiator 10 is cooled so as to face the upstream refrigerant path 17A of the first radiator 4 as shown in FIG. It is arranged on the upstream side of the wind. The temperature of the refrigerant in the second radiator 10 is set to be equal to or lower than the temperature of the refrigerant in the upstream refrigerant path 17 </ b> A of the first radiator 4.

このため、第２放熱器１０を通過した冷却風は、第２放熱器１０内の冷媒の温度より温度が高くなることはなく、第２放熱器１０を通過した冷却風で第１放熱器４の上流側冷媒パス１７Ａを冷却することができる。また、第１放熱器４の中間冷媒パス１７Ｂおよび下流側冷媒パス１７Ｃの２つのパスでは、第２放熱器１０を通過しない冷却風で冷却されるため、上流側冷媒パス１７Ａ内を通過した冷媒を確実に冷却することができる。   For this reason, the temperature of the cooling air that has passed through the second radiator 10 does not become higher than the temperature of the refrigerant in the second radiator 10, and the first radiator 4 is the cooling air that has passed through the second radiator 10. The upstream refrigerant path 17A can be cooled. Further, in the two paths of the intermediate radiator path 17B and the downstream refrigerant path 17C of the first radiator 4, the refrigerant that has passed through the upstream refrigerant path 17A is cooled by the cooling air that does not pass through the second radiator 10. Can be reliably cooled.

このように、第１放熱器４の上流側冷媒パス１７Ａの冷却風上流側に対向する第２放熱器１０を配置し、第２放熱器１０の冷媒温度を上流側冷媒パス１７Ａの冷媒温度以下に設定したことにより、第１放熱器４では吸熱することがなく、第１放熱器４および第２放熱器１０の双方の熱交換器を成立させることができる。   Thus, the 2nd heat radiator 10 which opposes the cooling wind upstream of the upstream refrigerant path 17A of the 1st radiator 4 is arranged, and the refrigerant temperature of the 2nd radiator 10 is below the refrigerant temperature of the upstream refrigerant path 17A. Therefore, the first heat radiator 4 does not absorb heat, and the heat exchangers of both the first heat radiator 4 and the second heat radiator 10 can be established.

なお、熱交換システムの運転条件により、第１放熱器４と第２放熱器１０の冷媒温度は、絶対温度は変化するが、基本的に通常運転時は、吸熱を起こさないように制御することが可能である。   The refrigerant temperature of the first radiator 4 and the second radiator 10 varies depending on the operating conditions of the heat exchange system, but basically the temperature is controlled so as not to absorb heat during normal operation. Is possible.

また、第２放熱器１０を第１放熱器４に対向して冷却風を共用できる構成であるため、第２放熱器１０を別の場所に配置する必要がなく、例えばエンジンルーム内の省スペース化を図ることができる。   In addition, since the second radiator 10 is configured to be able to share the cooling air facing the first radiator 4, there is no need to arrange the second radiator 10 in another place, for example, space saving in the engine room. Can be achieved.

本実施の形態の熱交換システムにおいては、図５に示すように、第２放熱器１０の冷媒が流れる方向をヘッダ１８からヘッダ１９に向けて、第１放熱器４の上流側冷媒パス１７Ａと第２放熱器１０の高温側と低温側とを合わせることにより、第１放熱器４の上流側冷媒パス１７Ａ内で局部的に吸熱が起こることを防止でき、放熱効率を高めることができる。   In the heat exchange system of the present embodiment, as shown in FIG. 5, the direction in which the refrigerant of the second radiator 10 flows is directed from the header 18 to the header 19, and the upstream side refrigerant path 17 </ b> A of the first radiator 4 By combining the high temperature side and the low temperature side of the second radiator 10, local heat absorption can be prevented in the upstream refrigerant path 17 </ b> A of the first radiator 4, and the heat radiation efficiency can be improved.

（第２の実施の形態）
次に、本発明の第２の実施の形態に係る熱交換システムを図６を用いて説明する。なお、本実施の形態では、上述の第１の実施の形態の構成を大部分が同一であるため、異なる構成部分のみを説明する。 (Second Embodiment)
Next, a heat exchange system according to a second embodiment of the present invention will be described with reference to FIG. In the present embodiment, since the configuration of the first embodiment described above is mostly the same, only different components will be described.

図６に示すように、本実施の形態の熱交換システムにおいては、幅の狭い第２放熱器３０を第１放熱器４の冷却風上流側に配置したものである。この第２放熱器３０は、第１放熱器４の上流側冷媒パス１７Ａの冷媒入口１５側に近い部分に対向配置されている。   As shown in FIG. 6, in the heat exchange system of the present embodiment, the narrow second radiator 30 is arranged on the cooling air upstream side of the first radiator 4. The second radiator 30 is disposed opposite to a portion of the upstream refrigerant path 17A of the first radiator 4 that is close to the refrigerant inlet 15 side.

本実施の形態では、第２放熱器３０が第１放熱器４の冷媒温度の高い領域と対向するため、第２放熱器３０の冷媒温度より第１放熱器４の冷媒温度のほうが確実に高いため、第２放熱器３０を通過した冷却風により第１放熱器４で吸熱が確実に起こることがないように設定されている。   In the present embodiment, since the second radiator 30 faces the region where the refrigerant temperature of the first radiator 4 is high, the refrigerant temperature of the first radiator 4 is surely higher than the refrigerant temperature of the second radiator 30. Therefore, the first heat radiator 4 is set so that heat absorption does not occur reliably due to the cooling air that has passed through the second heat radiator 30.

（第３の実施の形態）
次に、本発明の第３の実施の形態に係る熱交換システムを図７および図８を用いて説明する。本実施の形態では、第２放熱器４０を第１放熱器４の冷却風下流側に配置したことを特徴としている。なお、本実施の形態における他の構成は、上述した第１の実施の形態と同様であるため、その説明は省略する。 (Third embodiment)
Next, a heat exchange system according to a third embodiment of the present invention will be described with reference to FIGS. The present embodiment is characterized in that the second heat radiator 40 is disposed on the cooling air downstream side of the first heat radiator 4. Since other configurations in the present embodiment are the same as those in the first embodiment described above, description thereof is omitted.

本実施の形態では、図７に示すように、第２放熱器４０を第１放熱器４の冷却風下流側で、第１放熱器４の下流側冷媒パス１７Ｃに対向するように配置している。この第２放熱器４０の幅寸法は、第１放熱器４の幅寸法とほぼ同一であり、ヘッダ４１、４１の長さ寸法は、ヘッダ１１、１２の三分の一に設定されている。ヘッダ４１、４２の互いの外側部には、冷媒出入口４１Ａ、４２Ａが設けられている。   In the present embodiment, as shown in FIG. 7, the second radiator 40 is arranged on the downstream side of the cooling air of the first radiator 4 so as to face the downstream refrigerant path 17 </ b> C of the first radiator 4. Yes. The width dimension of the second radiator 40 is substantially the same as the width dimension of the first radiator 4, and the length dimension of the headers 41 and 41 is set to one third of the headers 11 and 12. Refrigerant entrances 41A and 42A are provided on the outer sides of the headers 41 and 42, respectively.

このような構成において、第２放熱器４の下流側冷媒パス１７Ｃ内の冷媒温度は、第１放熱器４０内の冷媒温度以下になるように設定されている。このため、第１放熱器４の下流側冷媒パス１７Ｃを通過した冷却風は、第２放熱器４０内の冷媒の温度より温度が高くなることはなく、第１放熱器４の下流側冷媒パス１７Ｃを通過した冷却風で第２放熱器４０のを冷却することができる。また、第１放熱器４の冷却風上流側には放熱器が存在しないため、確実に冷却することができる。   In such a configuration, the refrigerant temperature in the downstream refrigerant path 17 </ b> C of the second radiator 4 is set to be equal to or lower than the refrigerant temperature in the first radiator 40. For this reason, the cooling air that has passed through the downstream refrigerant path 17 </ b> C of the first radiator 4 does not become higher than the temperature of the refrigerant in the second radiator 40, and the downstream refrigerant path of the first radiator 4. The second radiator 40 can be cooled by the cooling air that has passed through 17C. In addition, since there is no radiator on the cooling air upstream side of the first radiator 4, the first radiator 4 can be reliably cooled.

このように、第１放熱器４の下流側冷媒パス１７Ｃの冷却風下流側に対向する第２放熱器４０を配置し、下流側冷媒パス１７Ｃの冷媒温度が第２放熱器４０内の冷媒温度以下に設定されているため、第２放熱器４０では吸熱することがなく、第１放熱器４および第２放熱器４０の双方の熱交換器を成立させることができる。   As described above, the second radiator 40 facing the cooling air downstream side of the downstream refrigerant path 17C of the first radiator 4 is arranged, and the refrigerant temperature in the downstream refrigerant path 17C is the refrigerant temperature in the second radiator 40. Since it is set as follows, the second radiator 40 does not absorb heat, and both heat exchangers of the first radiator 4 and the second radiator 40 can be established.

なお、上述の第１および第２の実施の形態と同様に、熱交換システムの運転条件により、第１放熱器４と第２放熱器４０の冷媒温度は、絶対温度は変化するが、基本的に通常運転時は、吸熱を起こさないように制御することが可能である。   Similar to the first and second embodiments described above, the refrigerant temperature of the first radiator 4 and the second radiator 40 varies depending on the operating conditions of the heat exchange system. During normal operation, it is possible to control so as not to generate heat.

また、本実施の形態においても、第２放熱器４０を第１放熱器４に対向して冷却風を共用できる構成であるため、第２放熱器４０を別の場所に配置する必要がなく、例えばエンジンルーム内の省スペース化を図ることができる。   Also in the present embodiment, since the second radiator 40 is configured to be able to share the cooling air facing the first radiator 4, there is no need to arrange the second radiator 40 in another place, For example, space saving in the engine room can be achieved.

本実施の形態の熱交換システムにおいては、図８に示すように、第２放熱器４０の冷媒が流れる方向をヘッダ４２側からヘッダ４１側へ向けて、第１放熱器４の下流側冷媒パス１７Ｃと第２放熱器４０の高温側と低温側とを逆にすることにより、第２放熱器４０を効率的に冷却させることも可能である。なお、この場合も、第１放熱器４の下流側冷媒パス１７Ｃ内の冷媒温度は、第２放熱器４０内の冷媒温度以下に保たれていることが必要である。   In the heat exchange system of the present embodiment, as shown in FIG. 8, the refrigerant flow direction of the second radiator 40 flows from the header 42 side to the header 41 side, and the downstream refrigerant path of the first radiator 4. It is also possible to cool the second radiator 40 efficiently by reversing the high temperature side and the low temperature side of 17C and the second radiator 40. In this case also, the refrigerant temperature in the downstream refrigerant path 17C of the first radiator 4 needs to be kept below the refrigerant temperature in the second radiator 40.

なお、下流側冷媒パス１７Ｃは、図４に示すように、冷媒の流れ方向に沿って比較的緩やかに温度が低下するため、第２放熱器４０内の冷媒の流れ方向は、図８とは逆に下流側冷媒パス１７Ｃ内の冷媒の流れ方向と一致させてもよい。   As shown in FIG. 4, the downstream refrigerant path 17 </ b> C decreases in temperature relatively slowly along the refrigerant flow direction. Therefore, the refrigerant flow direction in the second radiator 40 is different from that in FIG. 8. On the contrary, the flow direction of the refrigerant in the downstream refrigerant path 17C may be matched.

（第４の実施の形態）
次に、本発明の第４の実施の形態に係る熱交換システムについて図９を用いて説明する。本実施の形態は、上述した第３の実施の形態とほぼ同様の構成であり、第２放熱器５０の幅寸法が第１放熱器４より短い場合である。 (Fourth embodiment)
Next, a heat exchange system according to a fourth embodiment of the present invention will be described with reference to FIG. The present embodiment has a configuration substantially similar to that of the above-described third embodiment, and is a case where the width dimension of the second radiator 50 is shorter than that of the first radiator 4.

本実施の形態では、第２放熱器５０の幅寸法が第１放熱器４の幅寸法の略半分であり、第１放熱器４の下流側冷媒パス１７Ｃのヘッダ１２側の領域に合わせて対向配置している。また、本実施の形態でも上述の第３の実施の形態と同様に、第２放熱器５０は、第１放熱器４の冷却風下流側に配置されている。   In the present embodiment, the width dimension of the second radiator 50 is substantially half of the width dimension of the first radiator 4 and is opposed to the area on the header 12 side of the downstream refrigerant path 17C of the first radiator 4. It is arranged. Also in the present embodiment, the second radiator 50 is arranged on the downstream side of the cooling air of the first radiator 4 as in the third embodiment.

また、第２放熱器５０のヘッダ５１、５２には、冷媒出入口５１Ａ、５２Ａが設けられている。なお、本実施の形態では、図４に示すように、第１放熱器４の冷媒温度の変動が少ない下流側冷媒パス１７Ｃの終端側の領域に、第２放熱器５０を対向配置しているため、第２放熱器５０の冷媒出入口５１Ａ、５２Ａのどちらを冷媒入口としてもよい。   The headers 51, 52 of the second radiator 50 are provided with refrigerant inlets / outlets 51A, 52A. In the present embodiment, as shown in FIG. 4, the second radiator 50 is disposed opposite to the terminal side region of the downstream refrigerant path 17 </ b> C where the refrigerant temperature of the first radiator 4 is small. Therefore, either the refrigerant inlet / outlet 51A or 52A of the second radiator 50 may be used as the refrigerant inlet.

（その他の実施の形態）
上述した実施の形態の開示の一部をなす論述および図面はこの発明を限定するものであると理解すべきではない。この開示から当業者には様々な代替実施の形態、実施例および運用技術が明らかとなろう。 (Other embodiments)
It should not be understood that the description and drawings which form part of the disclosure of the above-described embodiments limit the present invention. From this disclosure, various alternative embodiments, examples and operational techniques will be apparent to those skilled in the art.

例えば、上述した各実施の形態では、チューブが水平方向に沿って配置した状態を図示したが、第１放熱器４や第２放熱器１０、３０、４０、５０は上下左右の配置方向に限定されるものではない。   For example, in each of the above-described embodiments, the state in which the tubes are arranged in the horizontal direction is illustrated, but the first radiator 4 and the second radiators 10, 30, 40, and 50 are limited to the arrangement direction of the top, bottom, left, and right. Is not to be done.

また、上述した各実施の形態では、熱交換システムとして、二酸化炭素冷媒を用いる車両用空調システムを燃料電池自動車に適用した例であるが、本発明は、燃料電池自動車以外の車両や他の空調システムなどに適用可能である。   Further, in each of the above-described embodiments, the vehicle air conditioning system using a carbon dioxide refrigerant is applied to the fuel cell vehicle as the heat exchange system. However, the present invention is not limited to the fuel cell vehicle. It can be applied to systems.

さらに、上述した各実施の形態では、第１放熱器４が３つの冷媒パスをもつ場合で説明したが、単数でも３つ以外の複数でもよい。   Furthermore, although each embodiment mentioned above demonstrated the case where the 1st heat radiator 4 has three refrigerant | coolant paths, it may be single or multiple other than three.

また、上述した第３および第４の実施の形態では、第２放熱器４０，５０が熱交換器であるが、これに代えて電熱ヒータを配置する構成としてもよい。   In the third and fourth embodiments described above, the second radiators 40 and 50 are heat exchangers. However, instead of this, an electric heater may be arranged.

さらに、上述した各実施の形態では、第１放熱器４が図４に示す特性を持つ場合に適用して第２放熱器の配置を設定したが、冷媒が超臨界下で運転される冷凍サイクルの放熱器では図４に示した特性と同様の特性を持っているため、第１放熱器の特性に対応して第２放熱器の配置位置などを決定すればよい。   Furthermore, in each of the above-described embodiments, the arrangement of the second radiator is set by applying the first radiator 4 having the characteristics shown in FIG. 4, but the refrigeration cycle in which the refrigerant is operated under supercritical conditions. Since the radiator has the same characteristics as those shown in FIG. 4, the arrangement position of the second radiator may be determined in accordance with the characteristics of the first radiator.

本発明の熱交換システムの概略をを示す回路図である。It is a circuit diagram showing the outline of the heat exchange system of the present invention. 本発明の各実施の形態で用いる第１放熱器の斜視図である。It is a perspective view of the 1st radiator used in each embodiment of the present invention. 本発明の第１の実施の形態に係る熱交換システムの放熱器部分の斜視図である。It is a perspective view of the heat sink part of the heat exchange system which concerns on the 1st Embodiment of this invention. 本発明の各実施の形態で用いる第１放熱器における流路の位置と冷媒温度との関係を示す図である。It is a figure which shows the relationship between the position of the flow path in the 1st heat radiator used by each embodiment of this invention, and refrigerant | coolant temperature. 本発明の第１の実施の形態に係る熱交換システムにおける放熱器部分の斜視図である。It is a perspective view of a radiator part in a heat exchange system concerning a 1st embodiment of the present invention. 本発明の第２の実施の形態に係る熱交換システムにおける放熱器部分の斜視図である。It is a perspective view of the heat radiator part in the heat exchange system which concerns on the 2nd Embodiment of this invention. 本発明の第３の実施の形態に係る熱交換システムにおける放熱器部分の斜視図である。It is a perspective view of the heat radiator part in the heat exchange system which concerns on the 3rd Embodiment of this invention. 本発明の第３の実施の形態に係る熱交換システムにおける放熱器部分の斜視図である。It is a perspective view of the heat radiator part in the heat exchange system which concerns on the 3rd Embodiment of this invention. 本発明の第４の実施の形態に係る熱交換システムにおける放熱器部分の斜視図である。It is a perspective view of the heat radiator part in the heat exchange system which concerns on the 4th Embodiment of this invention.

符号の説明Explanation of symbols

４ 第１放熱器
１０，３０，４０，５０ 第２放熱器
１１，１２ ヘッダ
１３ チューブ
１４ フィン
１５ 冷媒入口
１６ 冷媒出口
１７ 冷媒パス
１７Ａ 上流側冷媒パス
１７Ｂ 中間冷媒パス
１７Ｃ 下流側冷媒パス
１８，１９，４１，４２，５１，５２ ヘッダ 4 1st heat radiator 10, 30, 40, 50 2nd heat radiator 11, 12 Header 13 Tube 14 Fin 15 Refrigerant inlet 16 Refrigerant outlet 17 Refrigerant path 17A Upstream refrigerant path 17B Intermediate refrigerant path 17C Downstream refrigerant path 18, 19 , 41, 42, 51, 52 Header

Claims (6)

冷媒が超臨界下で運転される冷凍サイクルの第１放熱器（４）と、該第１放熱器（４）の冷却風が通過する領域の一部（１７Ａ，１７Ｃ）に対向するように他の第２放熱器（１０，３０，４０，５０）とを、互いに放熱を維持するように配置させ、前記第１放熱器（４）における冷媒の下流側領域（１７Ｃ）に対向するように、前記第２放熱器（４０，５０）を前記第１放熱器（４）よりも冷却風の下流側に配置させたことを特徴とする熱交換システム。   The first radiator (4) of the refrigeration cycle in which the refrigerant is operated under supercriticality, and other parts of the first radiator (4) so as to face a part (17A, 17C) of the region through which the cooling air passes. The second radiator (10, 30, 40, 50) are arranged so as to maintain heat dissipation from each other, and face the downstream region (17C) of the refrigerant in the first radiator (4), The heat exchange system, wherein the second radiator (40, 50) is disposed downstream of the first radiator (4) in the cooling air. 冷媒が超臨界下で運転される冷凍サイクルの第１放熱器（４）と、該第１放熱器（４）の冷却風が通過する領域の一部（１７Ａ，１７Ｃ）に対向するように他の第２放熱器（１０，３０，４０，５０）と、を配置させると共に、
前記第１放熱器（４）と前記第２放熱器（１０，３０，４０，５０）とのうち、互いに対向する領域における内部冷媒の温度が低い方を冷却風の上流側に配置させ、前記第１放熱器（４）における冷媒の下流側領域（１７Ｃ）に対向するように、前記第２放熱器（４０，５０）を前記第１放熱器（４）よりも冷却風の下流側に配置させたことを特徴とする熱交換システム。 The first radiator (4) of the refrigeration cycle in which the refrigerant is operated under supercriticality, and the other (17A, 17C) so as to face part of the region (17A, 17C) through which the cooling air of the first radiator (4) passes. And the second radiator (10, 30, 40, 50) of
Of the first radiator (4) and the second radiator (10, 30, 40, 50), the one having the lower temperature of the internal refrigerant in the region facing each other is arranged on the upstream side of the cooling air, and The second radiator (40, 50) is arranged on the downstream side of the cooling air from the first radiator (4) so as to face the downstream region (17C) of the refrigerant in the first radiator (4). A heat exchange system characterized by 前記第２放熱器（４）の冷媒の流れ方向が前記下流側領域（１７Ｃ）における冷媒の流れ方向と逆方向であることを特徴とする請求項１又は請求項２いずれか一項に記載の熱交換システム。The flow direction of the refrigerant in the second radiator (4) is opposite to the flow direction of the refrigerant in the downstream region (17C). Heat exchange system. 前記第１放熱器（４）は、一対の平行なヘッダ（１１，１２）と、前記ヘッダ（１１，１２）間を結ぶ複数のチューブ（１３）と、前記チューブ（１３）間に配置されたフィン（１４）と、を備えてなることを特徴とする請求項１乃至請求項３のいずれか一項に記載された熱交換システム。The first radiator (4) is disposed between a pair of parallel headers (11, 12), a plurality of tubes (13) connecting the headers (11, 12), and the tubes (13). The heat exchange system according to any one of claims 1 to 3, further comprising a fin (14). 前記チューブ（１３）は、前記ヘッダ（１１，１２）の長手方向に沿って複数の冷媒パス（１７Ａ，１７Ｂ，１７Ｃ）に区分され、互いに隣接する前記冷媒パス（１７Ａ，１７Ｂ，１７Ｃ）同士は互いに異なる方向に冷媒を案内することを特徴とする請求項４記載の熱交換システム。The tube (13) is divided into a plurality of refrigerant paths (17A, 17B, 17C) along the longitudinal direction of the header (11, 12), and the adjacent refrigerant paths (17A, 17B, 17C) are adjacent to each other. The heat exchange system according to claim 4, wherein the refrigerant is guided in different directions. 前記第２放熱器（４０，５０）が電熱ヒータであることを特徴とする請求項１乃至請求項５のいずれか一項に記載された熱交換システム。The heat exchange system according to any one of claims 1 to 5, wherein the second radiator (40, 50) is an electric heater.
JP2004100266A 2004-03-30 2004-03-30 Heat exchange system Expired - Fee Related JP4355604B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004100266A JP4355604B2 (en) 2004-03-30 2004-03-30 Heat exchange system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2004100266A JP4355604B2 (en) 2004-03-30 2004-03-30 Heat exchange system

Publications (2)

Publication Number Publication Date
JP2005283021A JP2005283021A (en) 2005-10-13
JP4355604B2 true JP4355604B2 (en) 2009-11-04

Family

ID=35181610

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2004100266A Expired - Fee Related JP4355604B2 (en) 2004-03-30 2004-03-30 Heat exchange system

Country Status (1)

Country Link
JP (1) JP4355604B2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4889011B2 (en) * 2006-07-20 2012-02-29 株式会社Ｂ．Ｔ．Ｐ． Air conditioning system
FR2928448B1 (en) * 2008-03-04 2015-05-01 Valeo Systemes Thermiques IMPROVED GAS COOLER

Also Published As

Publication number Publication date
JP2005283021A (en) 2005-10-13

Similar Documents

Publication Publication Date Title
JP5626194B2 (en) Heat exchange system
US10962307B2 (en) Stacked heat exchanger
JP2008080995A (en) Cooling system
JP5775661B2 (en) Automotive heating, ventilation, and / or air conditioning
WO2013084465A1 (en) Heat exchange system
JP5274175B2 (en) Cold storage heat exchanger
JP2008180486A (en) Heat exchanger
JP2007232287A (en) Heat exchanger and integral type heat exchanger
JP2006329511A (en) Heat exchanger
JP4312039B2 (en) Vehicle air-conditioning technology with a supercritical refrigerant refrigeration cycle
JP2008111624A (en) Heat exchanger
JP5264442B2 (en) Air conditioner for vehicles
JP2006097911A (en) Heat exchanger
JP2004218983A (en) Heat exchanger
JP4355604B2 (en) Heat exchange system
WO2007063978A1 (en) Heat exchanger
US20180029438A1 (en) Device for heat transfer and method for operating the device
JP6537928B2 (en) Heat exchanger and heat pump system
US9834061B2 (en) Assembly including a heat exchanger and a mounting on which said exchanger is mounted
JP4107148B2 (en) Refrigeration cycle and heat exchanger
JP2006207835A (en) Refrigerating system, compressing and heat-radiating apparatus and heat radiator
JP4338592B2 (en) Heater unit
JP4338566B2 (en) Vehicle heat exchanger
JP6275046B2 (en) Refrigeration cycle and heat exchanger for vehicle air conditioning
JP2005009808A (en) Heat exchanger for air conditioner

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20060324

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20081028

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20081111

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20090108

A02 Decision of refusal

Free format text: JAPANESE INTERMEDIATE CODE: A02

Effective date: 20090331

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20090423

A911 Transfer of reconsideration by examiner before appeal (zenchi)

Free format text: JAPANESE INTERMEDIATE CODE: A911

Effective date: 20090601

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20090707

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20090803

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120807

Year of fee payment: 3

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130807

Year of fee payment: 4

LAPS Cancellation because of no payment of annual fees