WO2007034745A1 - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
WO2007034745A1
WO2007034745A1 PCT/JP2006/318376 JP2006318376W WO2007034745A1 WO 2007034745 A1 WO2007034745 A1 WO 2007034745A1 JP 2006318376 W JP2006318376 W JP 2006318376W WO 2007034745 A1 WO2007034745 A1 WO 2007034745A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchanger
pressure refrigerant
refrigerant
low
pressure
Prior art date
Application number
PCT/JP2006/318376
Other languages
French (fr)
Japanese (ja)
Inventor
Takayuki Setoguchi
Makoto Kojima
Original Assignee
Daikin Industries, Ltd.
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 Daikin Industries, Ltd. filed Critical Daikin Industries, Ltd.
Priority to EP06798039.1A priority Critical patent/EP1944562B1/en
Priority to US12/067,087 priority patent/US20090282861A1/en
Priority to AU2006293191A priority patent/AU2006293191B2/en
Priority to CN2006800342799A priority patent/CN101268312B/en
Publication of WO2007034745A1 publication Critical patent/WO2007034745A1/en

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Classifications

    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0016—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being bent
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve

Definitions

  • the present invention relates to an air conditioner using a supercooling heat exchanger.
  • FIG. 4 shows a configuration of an air conditioner using a conventional supercooling heat exchanger.
  • the air conditioner includes a compressor four-way switching valve 2, an outdoor side heat exchanger 3 that acts as a condenser during cooling operation and an evaporator during heating operation, a heating expansion valve 4, a receiver 5,
  • the cooling expansion valve 6 and the indoor unit side heat exchanger 8 that acts as an evaporator during the cooling operation and acts as a condenser during the heating operation are sequentially connected via the four-way switching valve 2 as shown in the figure. It constitutes a refrigeration cycle for air conditioning.
  • the switching operation of the four-way switching valve 2 allows the refrigerant to flow reversibly in the direction indicated by the solid arrow in the figure during cooling operation and in the direction indicated by the dotted arrow in the figure during heating operation. Thus, cooling or heating action is realized.
  • the outdoor unit side heat exchanger 3 and the indoor unit side heat exchanger 8 are each provided with a large number of refrigerant paths. Therefore, even if the refrigerant distribution performance of the flow divider portion is maximized, it is difficult to evenly distribute the refrigerant in each refrigerant path.
  • the heating expansion valve is used so that the outlet side refrigerant is in an appropriate wet state.
  • the pressure reduction amount of 4 or the cooling expansion valve 6 is set appropriately.
  • a liquid-gas heat exchanger 13 having a double pipe structure including a low-pressure refrigerant suction pipe 14 serving as an inner pipe and a high-pressure liquid refrigerant pipe 15 serving as an outer pipe is provided as a supercooling heat exchanger.
  • the refrigerant flow rate, the double tube length, the inner diameter of the outer tube, and the outer diameter of the inner tube are appropriately set in a predetermined relationship.
  • Patent Document 1 Japanese Patent Laid-Open No. 5-326441 (Specifications page 1-5, Fig. 1-5)
  • An overcooling heat exchanger is provided in an air conditioner including a supercooling heat exchanger that exchanges heat between a low-pressure refrigerant and a high-pressure refrigerant.
  • the heat exchanger is divided into the first and second heat exchangers, and one of the heat exchangers is arranged so that the high-pressure refrigerant and the low-pressure refrigerant face each other, while the other heat exchanger
  • An object of the present invention is to provide an air conditioner that appropriately solves the above-mentioned conventional problems by arranging the high-pressure refrigerant and the low-pressure refrigerant in parallel flow.
  • the present invention comprises the following problem solving means.
  • the problem-solving means of the present invention is an air conditioner having a supercooling heat exchanger 13 for exchanging heat between a low-pressure refrigerant and a high-pressure refrigerant, wherein the supercooling heat exchanger 13 is replaced with first and second two heat exchangers. 13A and 13B, and either one of the first heat exchanger 13A or the second heat exchanger 13B is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are opposed to each other, while the other side second heat Exchange
  • the heat exchanger 13B or the first heat exchanger 13A is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow.
  • the refrigerant flows in opposite directions during cooling and heating. There is a problem that the heat exchange efficiency deteriorates.
  • the supercooling heat exchange is divided into two heat exchangers, the first heat exchange l3A and the second heat exchanger 13B, and either one of the heat exchangers 13A or 13B is pressurized.
  • the refrigerant and the low-pressure refrigerant are arranged so as to face each other, and the other heat exchanger 13B or 13A is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow, the flow direction of the cooling medium is changed between cooling and heating. Even if it changes, the heat exchange performance of the supercooling heat exchanger 13 can be maintained without change.
  • the problem-solving means of the present invention is the configuration of the problem-solving means of the invention of claim 1, wherein the first and second heat exchangers 13A, 13B are respectively provided with a high-pressure liquid refrigerant pipe on the outer periphery of the low-pressure refrigerant suction pipe 14. It is characterized by striking 15.
  • the first and second heat exchangers 13A and 13B are configured so that the high-pressure liquid refrigerant pipe 15 is wound around the low-pressure refrigerant suction pipe 14, the volume of the heat exchanger itself is increased.
  • the supercooled heat exchanger 13B which is not necessary, can be made as small as possible.
  • the problem-solving means of the present invention is the same as the problem-solving means of the first aspect of the invention, wherein the first and second heat exchangers 13A and 13B are arranged on the outer periphery of the low-pressure refrigerant suction pipe 14, respectively.
  • a high-pressure liquid refrigerant pipe 15 having a diameter larger than that of the suction pipe 14 is fitted in a coaxial structure.
  • first and second heat exchangers 13A and 13B for supercooling have a double pipe structure in which the high pressure liquid refrigerant pipe 15 is fitted in the coaxial structure to the low pressure refrigerant suction pipe 14, respectively.
  • the structure of the subcooling heat exchangers 13A and 13B itself is simplified.
  • each heat exchanger is configured such that the high-pressure liquid refrigerant pipe is attached to the low-pressure refrigerant suction pipe, the supercooling heat exchanger itself can be miniaturized as much as possible.
  • FIG. 1 is a refrigeration circuit diagram showing a configuration of an air conditioner according to a best embodiment of the present invention.
  • FIG. 2 is an enlarged view of the first and second liquid-gas heat exchanger portions, which are the main parts of the apparatus.
  • FIG. 3 is an enlarged view of the first and second liquid-gas heat exchanger portions of an air conditioner according to another embodiment of the present invention.
  • FIG. 4 is a refrigeration circuit diagram showing a configuration of an air conditioner according to a conventional example.
  • [0011] 1 is a compressor, 2 is a four-way selector valve, 3 is an outdoor unit side heat exchanger, 4 and 6 are expansion valves, 5 is a receiver, 8 is an indoor unit side heat exchanger, and 13A is the first , 13B is a second heat exchanger, 14 is a low-pressure refrigerant suction pipe, 15 is a high-pressure liquid refrigerant pipe, and 16 is a muffler.
  • FIG. 1 and FIG. 2 of the attached drawings show the entire refrigeration circuit of the air-conditioning apparatus according to the best mode of the present invention and the configuration of the main part! / Speak.
  • the air conditioner of the present embodiment has a compressor 1, a four-way switching valve 2, an outdoor unit side heat exchange that acts as a condenser during cooling operation and acts as an evaporator during heating operation.
  • the above-mentioned four-way switching valve includes an air heater 3, an expansion valve for heating 4, a receiver 5, an expansion valve for cooling 6, and an indoor unit side heat exchanger 8 that functions as an evaporator during cooling operation and as a condenser during heating operation. 2 are connected in sequence to form an air-conditioning refrigeration cycle as shown.
  • the subcooling heat exchange is composed of the low-pressure refrigerant suction pipe 14 and the high-pressure liquid refrigerant pipe 15, and exchanges heat between the low-pressure refrigerant and the high-pressure refrigerant.
  • a liquid-gas heat exchanger ⁇ 13 is provided as a vessel.
  • the liquid-gas heat exchanger 13 differs from the case of FIG.
  • the first liquid-gas heat exchange l3A and the second The liquid-gas heat exchange ⁇ 13B is divided into two liquid-gas heat exchange ⁇ , for example, the first heat exchanger 13A is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are opposed to each other
  • the second heat exchanger 13B is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow.
  • the first and second liquid-gas heat exchanges l3A and 13B are respectively supplied from the indoor unit side heat exchanger (evaporator) 8 during cooling or from the outdoor unit side heat exchanger (evaporator) 3 during heating.
  • 15 is formed by spirally wrapping them in opposite directions. Therefore, the volume of the supercooling heat exchanger 13 itself is small, and the miniaturization is possible.
  • the divided first and second heat exchangers 13A and 13B are connected to the existing low-pressure refrigerant from the four-way switching valve 2 to the refrigerant suction port of the compressor 1.
  • the high-pressure liquid refrigerant pipe 15 having a small diameter is spirally wound around the suction pipe 14
  • the first and second heat exchangers 13A and 13B are, for example, as shown in FIG.
  • a high-pressure liquid refrigerant pipe 15 having a diameter larger than that of the low-pressure refrigerant suction pipe 14 is fitted to the coaxial structure on the outer periphery of the pipe 14, and they are arranged so that the refrigerant flows in the opposite direction to each other. You may have done.
  • the first and second heat exchangers 13A and 13B for supercooling are configured as a double pipe in which the high-pressure liquid refrigerant pipe 15 is fitted into the coaxial structure with respect to the low-pressure refrigerant suction pipe 14, respectively. This simplifies the structure of the subcooling heat exchanger itself.
  • the present invention can be widely used in the field of air conditioners using a supercooling heat exchanger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

In the supercooling heat exchanger of an air conditioner for exchanging heat between high pressure refrigerant and low pressure refrigerant, a flow direction of refrigerant during a cooling operation is reversed during a heating operation to cause the high pressure refrigerant and the low pressure refrigerant to flow in parallel in either one operation mode, whereby a heat exchange efficiency deteriorates. In an air conditioner comprising a supercooling heat exchanger (13) for exchanging heat between low pressure refrigerant and high pressure refrigerant, the supercooling heat exchanger (13) is divided into first and second heat exchangers (13A, 13B), any one of the first heat exchanger (13A) and the second heat exchanger (13B) is arranged such that the high pressure refrigerant and the low pressure refrigerant produce counter flows, and the second heat exchanger (13B) or the first heat exchanger (13A) on the other side is arranged such that the high pressure refrigerant and the low pressure refrigerant produce parallel flows. Each heat exchanger (13A, 13B) is arranged such that a high pressure liquid refrigerant tube (15) is wound around the outer periphery of a suction tube (14) for sucking low pressure refrigerant thus reducing each size.

Description

明 細 書  Specification
空気調和装置  Air conditioner
技術分野  Technical field
[0001] 本願発明は、過冷却熱交換器を用いた空気調和装置に関するものである。  [0001] The present invention relates to an air conditioner using a supercooling heat exchanger.
背景技術  Background art
[0002] 図 4は、従来の過冷却熱交換器を用いた空気調和装置の構成を示して 、る。  FIG. 4 shows a configuration of an air conditioner using a conventional supercooling heat exchanger.
同空気調和装置は、圧縮機 四路切換弁 2、冷房運転時に凝縮器として作用し、 暖房運転時に蒸発器として作用する室外機側熱交換器 3、暖房用膨張弁 4、レシ一 バー 5、冷房用膨張弁 6、および冷房運転時に蒸発器として作用し、暖房運転時に 凝縮器として作用する室内機側熱交 8等を上記四路切換弁 2を介して順次接続 して、図示のような空気調和用の冷凍サイクルを構成している。  The air conditioner includes a compressor four-way switching valve 2, an outdoor side heat exchanger 3 that acts as a condenser during cooling operation and an evaporator during heating operation, a heating expansion valve 4, a receiver 5, The cooling expansion valve 6 and the indoor unit side heat exchanger 8 that acts as an evaporator during the cooling operation and acts as a condenser during the heating operation are sequentially connected via the four-way switching valve 2 as shown in the figure. It constitutes a refrigeration cycle for air conditioning.
そして、上記四路切換弁 2の切換作動により、冷房運転時には図中に実線矢印で 示す方向に、また暖房運転時には同図中に点線矢印で示す方向に、それぞれ冷媒 が可逆的に流通せしめられて、冷房又は暖房作用が実現される。  The switching operation of the four-way switching valve 2 allows the refrigerant to flow reversibly in the direction indicated by the solid arrow in the figure during cooling operation and in the direction indicated by the dotted arrow in the figure during heating operation. Thus, cooling or heating action is realized.
上記室外機側熱交換器 3および室内機側熱交換器 8は、それぞれ多数の冷媒パス を備えて構成されている。したがって、分流器部分の冷媒分配性能を最大限に向上 させたとしても、各冷媒パスの冷媒の均等な分配が困難となる。  The outdoor unit side heat exchanger 3 and the indoor unit side heat exchanger 8 are each provided with a large number of refrigerant paths. Therefore, even if the refrigerant distribution performance of the flow divider portion is maximized, it is difficult to evenly distribute the refrigerant in each refrigerant path.
[0003] そこで、室外機側熱交 3又は室内機側熱交 8を蒸発器として作用させて いる場合には、それらの出口側冷媒が適切な湿り状態となるように、上記暖房用膨張 弁 4又は冷房用膨張弁 6の減圧量が適切に設定されている。そのようにすると、室外 機側熱交換器 3又は室内機側熱交換器 8に例えば冷媒の偏流が生じたとしても、蒸 発器としての能力が最大限に確保されることになり、蒸発器の可及的なコンパクトィ匕 が図られる。 [0003] Therefore, when the outdoor unit side heat exchanger 3 or the indoor unit side heat exchanger 8 is operated as an evaporator, the heating expansion valve is used so that the outlet side refrigerant is in an appropriate wet state. The pressure reduction amount of 4 or the cooling expansion valve 6 is set appropriately. As a result, even if, for example, a refrigerant drift occurs in the outdoor unit-side heat exchanger 3 or the indoor unit-side heat exchanger 8, the capability of the evaporator is ensured to the maximum, and the evaporator As much compactness as possible is achieved.
また、一方凝縮器出口側冷媒の過冷却をとり、蒸発器側のェンタルピ差を拡大して 循環量を落とし、蒸発器側の圧損を低減することによって、さらなる蒸発器の性能向 上を図るために、過冷却熱交^^として内管となる低圧冷媒吸入管 14と外管となる 高圧液冷媒管 15とからなる二重管構造の液—ガス熱交翻13が設けられている。 この液-ガス熱交換器 13は、例えば冷媒流量、二重管長さ、外管の内径、内管の 外径が、所定の関係で適切に設定されている。 On the other hand, to further improve the performance of the evaporator by supercooling the refrigerant on the outlet side of the condenser, expanding the enthalpy difference on the evaporator side, reducing the circulation rate, and reducing the pressure loss on the evaporator side. In addition, a liquid-gas heat exchanger 13 having a double pipe structure including a low-pressure refrigerant suction pipe 14 serving as an inner pipe and a high-pressure liquid refrigerant pipe 15 serving as an outer pipe is provided as a supercooling heat exchanger. In the liquid-gas heat exchanger 13, for example, the refrigerant flow rate, the double tube length, the inner diameter of the outer tube, and the outer diameter of the inner tube are appropriately set in a predetermined relationship.
[0004] このように液 ガス熱交換器 13が設けられていると、蒸発器出口側の冷媒が過熱 され、圧縮機 1への液バックを防止することができるとともに、凝縮器出口側の冷媒が 過冷却され、蒸発器側のェンタルピ差を拡大して冷媒の循環量を落とすことができる ので、その圧損も低減でき、蒸発器 8 (または蒸発器 3)のさらなるコンパクトィ匕を図る ことができる（一例として特許文献 1参照)。 [0004] When the liquid gas heat exchanger 13 is provided as described above, the refrigerant on the evaporator outlet side is overheated, so that liquid back to the compressor 1 can be prevented and the refrigerant on the condenser outlet side is prevented. Since the refrigerant is supercooled and the enthalpy difference on the evaporator side can be enlarged to reduce the circulation amount of the refrigerant, the pressure loss can be reduced and the evaporator 8 (or the evaporator 3) can be further compacted. Yes (see Patent Document 1 as an example).
特許文献 1 :特開平 5— 332641号公報（明細書 1—5頁、図 1— 5)  Patent Document 1: Japanese Patent Laid-Open No. 5-326441 (Specifications page 1-5, Fig. 1-5)
発明の開示  Disclosure of the invention
発明が解決しょうとする課題  Problems to be solved by the invention
[0005] ところが、上記のように高圧冷媒と低圧冷媒を熱交換する過冷却熱交換器にお 、 ては、冷房時と暖房時で冷媒の流れる方向が逆になるため、どちらかの運転モード において、それらが平行流となり、熱交換効率が悪くなる問題がある。例えば図 4の 場合、冷房時は対向流であるが暖房時は平行流となり、熱交換効率が落ちる。 [0005] However, in the supercooling heat exchanger that exchanges heat between the high-pressure refrigerant and the low-pressure refrigerant as described above, the refrigerant flows in opposite directions during cooling and heating. However, there is a problem that they become parallel flows and heat exchange efficiency deteriorates. For example, in the case of Fig. 4, the counter flow during cooling is parallel flow during heating, and the heat exchange efficiency decreases.
本願発明は、このような問題を解決するためになされたもので、低圧冷媒と高圧冷 媒を熱交換する過冷却熱交換器を備えた空気調和装置にぉ 、て、過冷却熱交換器 を第 1,第 2の 2つの熱交換器に分割し、それらの内の何れか一方側の熱交換器は 高圧冷媒と低圧冷媒が対向流になるように配置する一方、他方側の熱交換器は高 圧冷媒と低圧冷媒が平行流となるように配置することによって、上記従来の問題を適 切に解決した空気調和装置を提供することを目的とするものである。  The present invention has been made to solve such a problem. An overcooling heat exchanger is provided in an air conditioner including a supercooling heat exchanger that exchanges heat between a low-pressure refrigerant and a high-pressure refrigerant. The heat exchanger is divided into the first and second heat exchangers, and one of the heat exchangers is arranged so that the high-pressure refrigerant and the low-pressure refrigerant face each other, while the other heat exchanger An object of the present invention is to provide an air conditioner that appropriately solves the above-mentioned conventional problems by arranging the high-pressure refrigerant and the low-pressure refrigerant in parallel flow.
課題を解決するための手段  Means for solving the problem
[0006] 本願発明は、同目的を達成するために、次のような課題解決手段を備えて構成さ れている。 [0006] In order to achieve the object, the present invention comprises the following problem solving means.
(1) 請求項 1の発明  (1) Invention of claim 1
この発明の課題解決手段は、低圧冷媒と高圧冷媒を熱交換する過冷却熱交換器 1 3を備えた空気調和装置において、過冷却熱交換器 13を第 1,第 2の 2つの熱交換 器 13A, 13Bに分割し、第 1の熱交換器 13A又は第 2の熱交換器 13Bの何れか一 方を高圧冷媒と低圧冷媒が対向流になるように配置する一方、他方側第 2の熱交換 器 13B又は第 1の熱交 l3Aを高圧冷媒と低圧冷媒が平行流となるように配置し たことを特徴としている。 The problem-solving means of the present invention is an air conditioner having a supercooling heat exchanger 13 for exchanging heat between a low-pressure refrigerant and a high-pressure refrigerant, wherein the supercooling heat exchanger 13 is replaced with first and second two heat exchangers. 13A and 13B, and either one of the first heat exchanger 13A or the second heat exchanger 13B is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are opposed to each other, while the other side second heat Exchange The heat exchanger 13B or the first heat exchanger 13A is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow.
前述のように高圧冷媒と低圧冷媒を熱交換する過冷却熱交換器 13では、冷房時と 暖房時で冷媒の流れる方向が逆になるため、どちらかの運転モードにおいて、それ らが平行流となり、熱交換効率が悪くなる問題がある。  As described above, in the supercooling heat exchanger 13 that exchanges heat between the high-pressure refrigerant and the low-pressure refrigerant, the refrigerant flows in opposite directions during cooling and heating. There is a problem that the heat exchange efficiency deteriorates.
ところが、上記のように、当該過冷却熱交 を第 1の熱交 l3Aと第 2の熱 交換器 13Bとの 2つの熱交換器に分割し、何れか一方の熱交換器 13A又は 13Bを 高圧冷媒と低圧冷媒が対向流になるように配置する一方、他方側の熱交換器 13B 又は 13Aを高圧冷媒と低圧冷媒が平行流となるように配置すると、冷房と暖房で冷 媒の流れ方向が変化しても、変わりなく過冷却熱交換器 13の熱交換性能を維持する ことがでさるよう〖こなる。  However, as described above, the supercooling heat exchange is divided into two heat exchangers, the first heat exchange l3A and the second heat exchanger 13B, and either one of the heat exchangers 13A or 13B is pressurized. When the refrigerant and the low-pressure refrigerant are arranged so as to face each other, and the other heat exchanger 13B or 13A is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow, the flow direction of the cooling medium is changed between cooling and heating. Even if it changes, the heat exchange performance of the supercooling heat exchanger 13 can be maintained without change.
[0007] (2) 請求項 2の発明 [0007] (2) Invention of Claim 2
この発明の課題解決手段は、上記請求項 1の発明の課題解決手段の構成におい て、第 1,第 2の熱交換器 13A, 13Bは、それぞれ低圧冷媒吸入管 14の外周に高圧 液冷媒管 15を卷きつけて構成されていることを特徴としている。  The problem-solving means of the present invention is the configuration of the problem-solving means of the invention of claim 1, wherein the first and second heat exchangers 13A, 13B are respectively provided with a high-pressure liquid refrigerant pipe on the outer periphery of the low-pressure refrigerant suction pipe 14. It is characterized by striking 15.
このように、第 1,第 2の熱交換器 13A, 13Bを、それぞれ低圧冷媒吸入管 14に対 して高圧液冷媒管 15を巻きつけた構成にすると、熱交換器自体の容積を大きくする 必要がなぐ過冷却熱交翻13ん 13Bの可及的な小型化を図ることができる。  As described above, when the first and second heat exchangers 13A and 13B are configured so that the high-pressure liquid refrigerant pipe 15 is wound around the low-pressure refrigerant suction pipe 14, the volume of the heat exchanger itself is increased. The supercooled heat exchanger 13B, which is not necessary, can be made as small as possible.
[0008] (3) 請求項 3の発明 [0008] (3) Invention of Claim 3
この発明の課題解決手段は、上記請求項 1の発明の課題解決手段の構成におい て、第 1,第 2の熱交換器 13A, 13Bは、それぞれ低圧冷媒吸入管 14の外周に同低 圧冷媒吸入管 14よりも大径の高圧液冷媒管 15を同軸構造に嵌合して構成されてい ることを特徴としている。  The problem-solving means of the present invention is the same as the problem-solving means of the first aspect of the invention, wherein the first and second heat exchangers 13A and 13B are arranged on the outer periphery of the low-pressure refrigerant suction pipe 14, respectively. A high-pressure liquid refrigerant pipe 15 having a diameter larger than that of the suction pipe 14 is fitted in a coaxial structure.
このように、過冷却用の第 1,第 2の熱交換器 13A, 13Bを、それぞれ低圧冷媒吸 入管 14に対して高圧液冷媒管 15を同軸構造に嵌合した二重管構造にすると、過冷 却熱交換器 13A, 13B自体の構造が簡単になる。  As described above, when the first and second heat exchangers 13A and 13B for supercooling have a double pipe structure in which the high pressure liquid refrigerant pipe 15 is fitted in the coaxial structure to the low pressure refrigerant suction pipe 14, respectively. The structure of the subcooling heat exchangers 13A and 13B itself is simplified.
発明の効果  The invention's effect
[0009] 以上の結果、本願発明によると、冷房と暖房で冷媒の流れ方向が変化しても、過冷 却熱交^^の高い熱交換性能を維持することができる。その結果、蒸発器のさらなる コンパクトィ匕を図ることができる。 As a result of the above, according to the present invention, even if the flow direction of the refrigerant changes between cooling and heating, the supercooling is performed. High heat exchange performance with heat rejection can be maintained. As a result, further compactness of the evaporator can be achieved.
またその場合において、各熱交換器を、低圧冷媒の吸入管に対して高圧液冷媒管 を卷きつける構成にすると、可及的に過冷却熱交換器自体の小型化が図られる。 図面の簡単な説明  In this case, if each heat exchanger is configured such that the high-pressure liquid refrigerant pipe is attached to the low-pressure refrigerant suction pipe, the supercooling heat exchanger itself can be miniaturized as much as possible. Brief Description of Drawings
[0010] [図 1]図 1は、本願発明の最良の実施の形態に係る空気調和装置の構成を示す冷凍 回路図である。  FIG. 1 is a refrigeration circuit diagram showing a configuration of an air conditioner according to a best embodiment of the present invention.
[図 2]図 2は、同装置の要部である第 1,第 2の 2つの液 ガス熱交換器部分の拡大 図である。  [FIG. 2] FIG. 2 is an enlarged view of the first and second liquid-gas heat exchanger portions, which are the main parts of the apparatus.
[図 3]図 3は、本願発明のその他の実施の形態に係る空気調和装置の第 1,第 2の 2 つの液 ガス熱交換器部分の拡大図である。  FIG. 3 is an enlarged view of the first and second liquid-gas heat exchanger portions of an air conditioner according to another embodiment of the present invention.
[図 4]図 4は、従来例に係る空気調和装置の構成を示す冷凍回路図である。  FIG. 4 is a refrigeration circuit diagram showing a configuration of an air conditioner according to a conventional example.
符号の説明  Explanation of symbols
[0011] 1は圧縮機、 2は四路切換弁、 3は室外機側熱交換器、 4, 6は膨張弁、 5はレシ一 バー、 8は室内機側熱交換器、 13Aは第 1の熱交換器、 13Bは第 2の熱交換器、 14 は低圧冷媒吸入管、 15は高圧液冷媒管、 16はマフラーである。  [0011] 1 is a compressor, 2 is a four-way selector valve, 3 is an outdoor unit side heat exchanger, 4 and 6 are expansion valves, 5 is a receiver, 8 is an indoor unit side heat exchanger, and 13A is the first , 13B is a second heat exchanger, 14 is a low-pressure refrigerant suction pipe, 15 is a high-pressure liquid refrigerant pipe, and 16 is a muffler.
発明を実施するための最良の形態  BEST MODE FOR CARRYING OUT THE INVENTION
[0012] 添付した図面の図 1および図 2は、本願発明の最良の実施の形態に係る空気調和 装置の冷凍回路の全体および要部の構成を示して！/ヽる。 [0012] FIG. 1 and FIG. 2 of the attached drawings show the entire refrigeration circuit of the air-conditioning apparatus according to the best mode of the present invention and the configuration of the main part! / Speak.
本実施の形態の空気調和装置は、先ず図 1に示すように、圧縮機 1、四路切換弁 2 、冷房運転時に凝縮器として作用し、暖房運転時に蒸発器として作用する室外機側 熱交換器 3、暖房用膨張弁 4、レシーバー 5、冷房用膨張弁 6、および冷房運転時に 蒸発器として作用し、暖房運転時に凝縮器として作用する室内機側熱交換器 8等を 上記四路切換弁 2を介して順次接続して、図示のような空気調和用の冷凍サイクル を構成している。  First, as shown in FIG. 1, the air conditioner of the present embodiment has a compressor 1, a four-way switching valve 2, an outdoor unit side heat exchange that acts as a condenser during cooling operation and acts as an evaporator during heating operation. The above-mentioned four-way switching valve includes an air heater 3, an expansion valve for heating 4, a receiver 5, an expansion valve for cooling 6, and an indoor unit side heat exchanger 8 that functions as an evaporator during cooling operation and as a condenser during heating operation. 2 are connected in sequence to form an air-conditioning refrigeration cycle as shown.
そして、上記四路切換弁 2の切換作動により、冷房運転時には図中に実線矢印で 示す方向に、また暖房運転時には同図中に点線矢印で示す方向に、それぞれ冷媒 が可逆的に流通せしめられて、冷房又は暖房作用が実現される。 [0013] そして、本実施の形態でも、前述の図 4の場合と同様に、低圧冷媒の吸入管 14と 高圧液冷媒管 15とからなり、低圧冷媒と高圧冷媒を熱交換する過冷却熱交換器とし ての液—ガス熱交^^ 13が設けられている。 The switching operation of the four-way switching valve 2 allows the refrigerant to flow reversibly in the direction indicated by the solid arrow in the figure during cooling operation and in the direction indicated by the dotted arrow in the figure during heating operation. Thus, cooling or heating action is realized. [0013] In the present embodiment as well, as in the case of Fig. 4 described above, the subcooling heat exchange is composed of the low-pressure refrigerant suction pipe 14 and the high-pressure liquid refrigerant pipe 15, and exchanges heat between the low-pressure refrigerant and the high-pressure refrigerant. A liquid-gas heat exchanger ^^ 13 is provided as a vessel.
このように液—ガス熱交 が設けられて 、ると、すでに述べたように蒸発器出 口側の冷媒が過熱され、圧縮機 1への液バックを防止することができるとともに、凝縮 器出口側の冷媒が過冷却され、蒸発器側のェンタルピ差を拡大して冷媒の循環量 を落とすことができるので、その圧損も低減でき、蒸発器 (冷房時の室内機側熱交換 器 8又は暖房時の室外機側熱交翻3)の可及的なコンパクトィ匕を図ることができる。 しかし、本実施の形態の場合には、同液—ガス熱交換器 13は、前述の図 4の場合 とは異なり、相互に逆方向に冷媒が流れる第 1の液 ガス熱交 l3Aと第 2の液 —ガス熱交^^ 13Bとの 2つの液—ガス熱交^^に分割され、例えば第 1の熱交換 器 13Aは高圧冷媒と低圧冷媒が対向流になるように配置されている一方、第 2の熱 交 l3Bは高圧冷媒と低圧冷媒が平行流となるように配置されている。  If the liquid-gas heat exchange is provided in this way, the refrigerant on the evaporator outlet side is overheated as described above, and liquid back to the compressor 1 can be prevented, and the condenser outlet The refrigerant on the side is supercooled and the enthalpy difference on the evaporator side can be expanded to reduce the circulation amount of the refrigerant, so that the pressure loss can be reduced, and the evaporator (the indoor unit side heat exchanger 8 during cooling or heating) The outdoor unit side heat exchange 3) can be made as compact as possible. However, in the case of the present embodiment, the liquid-gas heat exchanger 13 differs from the case of FIG. 4 described above in that the first liquid-gas heat exchange l3A and the second The liquid-gas heat exchange ^^ 13B is divided into two liquid-gas heat exchange ^^, for example, the first heat exchanger 13A is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are opposed to each other The second heat exchanger 13B is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow.
[0014] したがって、このような構成では、冷房時と暖房時で冷媒の流れる方向が変化して も、図示の如ぐ変わりなく液—ガス熱交 の性能を維持することができる。その 結果、暖房時にも変りなく凝縮器出口側の冷媒が過冷却され、蒸発器側のェンタル ピ差を拡大して冷媒の循環量を落とすことができる。 [0014] Therefore, in such a configuration, even if the direction in which the refrigerant flows changes during cooling and heating, the liquid-gas heat exchange performance can be maintained without change as shown in the figure. As a result, the refrigerant on the outlet side of the condenser is subcooled without changing during heating, and the enthalpy difference on the evaporator side can be increased to reduce the circulation amount of the refrigerant.
し力も同第 1,第 2の液—ガス熱交 l3A, 13Bは、それぞれ冷房時の室内機側 熱交換器 (蒸発器) 8又は暖房時の室外機側熱交換器 (蒸発器) 3から四路切換弁 2 を介して圧縮機 1の冷媒吸入口に戻る既存の低圧冷媒吸入管 14の外周に対して、 同低圧冷媒吸入管 14よりも小径の凝縮器出口側力もの高圧液冷媒管 15を、例えば 図 2に詳細に示すように、相互に逆向きで螺旋状に巻きつけることにより構成されて いる。そのため、過冷却熱交換器 13自体の容積も小さぐ可及的な小型化が図られ る。  The first and second liquid-gas heat exchanges l3A and 13B are respectively supplied from the indoor unit side heat exchanger (evaporator) 8 during cooling or from the outdoor unit side heat exchanger (evaporator) 3 during heating. A high-pressure liquid refrigerant pipe having a smaller outlet pressure than the low-pressure refrigerant suction pipe 14 with respect to the outer periphery of the existing low-pressure refrigerant suction pipe 14 returning to the refrigerant suction port of the compressor 1 through the four-way switching valve 2 As shown in detail in FIG. 2, for example, 15 is formed by spirally wrapping them in opposite directions. Therefore, the volume of the supercooling heat exchanger 13 itself is small, and the miniaturization is possible.
[0015] また、過冷却熱交換効率の向上により、蒸発器自体の小型、コンパクト化にも有効 に寄与し得る。  [0015] Further, by improving the supercooling heat exchange efficiency, it is possible to effectively contribute to the miniaturization and downsizing of the evaporator itself.
さらに、図 2のように既存の低圧冷媒吸入管 14に巻くことで、吸入ガス圧損の上昇 を抑えることができ、 COPの低下をなくすことが可能である。 なお、図 2中の符号 16は、低圧冷媒吸入管 14におけるガス冷媒用のマフラーであ る。 Furthermore, as shown in FIG. 2, by winding it around the existing low-pressure refrigerant suction pipe 14, it is possible to suppress an increase in intake gas pressure loss and to eliminate a decrease in COP. 2 is a muffler for gas refrigerant in the low-pressure refrigerant suction pipe 14.
(その他の実施の形態）  (Other embodiments)
以上の実施の形態では、図 2に示すように、分割された第 1,第 2の熱交換器 13A, 13Bを、四方切換弁 2から圧縮機 1の冷媒吸入口に到る既存の低圧冷媒吸入管 14 に対して細径の高圧液冷媒管 15を螺旋状に巻き付ける構造としたが、同第 1,第 2 の熱交換器 13A, 13Bは、例えば図 3に示すように、低圧冷媒吸入管 14の外周に同 低圧冷媒吸入管 14よりも大径の高圧液冷媒管 15を同軸構造に嵌合した二重管構 造のものとして、それらを相互に冷媒が逆向きに流れるように配置したものでもよい。  In the above embodiment, as shown in FIG. 2, the divided first and second heat exchangers 13A and 13B are connected to the existing low-pressure refrigerant from the four-way switching valve 2 to the refrigerant suction port of the compressor 1. Although the high-pressure liquid refrigerant pipe 15 having a small diameter is spirally wound around the suction pipe 14, the first and second heat exchangers 13A and 13B are, for example, as shown in FIG. A high-pressure liquid refrigerant pipe 15 having a diameter larger than that of the low-pressure refrigerant suction pipe 14 is fitted to the coaxial structure on the outer periphery of the pipe 14, and they are arranged so that the refrigerant flows in the opposite direction to each other. You may have done.
[0016] このように、過冷却用の第 1,第 2の熱交換器 13A, 13Bを、それぞれ低圧冷媒吸 入管 14に対して高圧液冷媒管 15を同軸構造に嵌合した二重管構成にすると、過冷 却熱交換器自体の構造が簡単になる。 [0016] In this manner, the first and second heat exchangers 13A and 13B for supercooling are configured as a double pipe in which the high-pressure liquid refrigerant pipe 15 is fitted into the coaxial structure with respect to the low-pressure refrigerant suction pipe 14, respectively. This simplifies the structure of the subcooling heat exchanger itself.
産業上の利用分野  Industrial application fields
[0017] 本願発明は、過冷却熱交換器を用いた空気調和装置の分野において広く利用す ることが可能である。  [0017] The present invention can be widely used in the field of air conditioners using a supercooling heat exchanger.

Claims

請求の範囲 The scope of the claims
[1] 低圧冷媒と高圧冷媒を熱交換する過冷却熱交換器 (13)を備えた空気調和装置に おいて、過冷却熱交換器（13)を第 1,第 2の 2つの熱交換器（13A) , (13B)に分割 し、第 1の熱交換器（ 13 A)又は第 2の熱交換器 (13B)の何れか一方を高圧冷媒と 低圧冷媒が対向流になるように配置する一方、他方側第 2の熱交換器（13B)又は第 1の熱交 (13A)を高圧冷媒と低圧冷媒が平行流となるように配置したことを特徴 とする空気調和装置。  [1] In an air conditioner equipped with a supercooling heat exchanger (13) for exchanging heat between low-pressure refrigerant and high-pressure refrigerant, the supercooling heat exchanger (13) is replaced with the first and second heat exchangers. (13A) and (13B) are divided, and either the first heat exchanger (13A) or the second heat exchanger (13B) is arranged so that the high-pressure refrigerant and the low-pressure refrigerant face each other On the other hand, an air conditioner characterized in that the second heat exchanger (13B) or the first heat exchanger (13A) on the other side is arranged so that the high-pressure refrigerant and the low-pressure refrigerant are in parallel flow.
[2] 第 1,第 2の熱交換器（13A) , (13B)は、それぞれ低圧冷媒吸入管（14)の外周に 高圧液冷媒管（15)を巻きつけて構成されていることを特徴とする請求項 1記載の空 気調和装置。  [2] The first and second heat exchangers (13A) and (13B) are configured by wrapping a high-pressure liquid refrigerant pipe (15) around the outer periphery of the low-pressure refrigerant suction pipe (14), respectively. The air conditioning apparatus according to claim 1.
[3] 第 1,第 2の熱交換器（13A) , (13B)は、それぞれ低圧冷媒吸入管（14)の外周に 同低圧冷媒吸入管（14)よりも大径の高圧液冷媒管 15を同軸構造に嵌合して構成さ れて 、ることを特徴とする請求項 1記載の空気調和装置。  [3] The first and second heat exchangers (13A) and (13B) are respectively connected to the outer periphery of the low-pressure refrigerant suction pipe (14) with a high-pressure liquid refrigerant pipe having a larger diameter than the low-pressure refrigerant suction pipe (14). 2. The air conditioner according to claim 1, wherein the air conditioner is configured to be fitted in a coaxial structure.
PCT/JP2006/318376 2005-09-22 2006-09-15 Air conditioner WO2007034745A1 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10597446B2 (en) 2013-09-13 2020-03-24 Genentech, Inc. Method of treatment comprising purified recombinant IL-13 antibody

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2008304078A (en) * 2007-06-05 2008-12-18 Denso Corp Refrigerating cycle device
US8291719B2 (en) * 2007-10-09 2012-10-23 Be Aerospace, Inc. Thermal control system and method
JP2009115415A (en) * 2007-11-08 2009-05-28 Calsonic Kansei Corp Supercritical refrigerating cycle
JP4947043B2 (en) * 2008-07-14 2012-06-06 ダイキン工業株式会社 Outdoor unit for air conditioner and method for manufacturing the same
DK176868B1 (en) * 2008-09-16 2010-02-01 Lars Christian Wulf Zimmermann Symmetrical refrigerant regulator for flooded multi-channel evaporator
ATE554643T1 (en) * 2009-08-05 2012-05-15 Abb Research Ltd EVAPORATOR AND COOLING CIRCUIT
CN102597658B (en) * 2009-10-27 2014-10-22 三菱电机株式会社 Heat pump
JP5762427B2 (en) * 2010-10-12 2015-08-12 三菱電機株式会社 Air conditioner
JP2012097957A (en) * 2010-11-02 2012-05-24 Showa Denko Kk Intermediate heat exchanger
CN102095271A (en) * 2011-03-01 2011-06-15 四川长虹空调有限公司 Heat pump air conditioner
DE102012204404B4 (en) * 2011-03-25 2022-09-08 Denso Corporation heat exchange system and vehicle refrigeration cycle system
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KR20190055614A (en) * 2017-11-15 2019-05-23 엘지전자 주식회사 Plate heat exchanger and Air conditioner having the same
AU2017442329B2 (en) * 2017-12-06 2021-07-15 Mitsubishi Electric Corporation Heat exchanger, refrigeration cycle apparatus and method of manufacturing heat exchanger
CN108302839A (en) * 2017-12-29 2018-07-20 青岛海尔空调器有限总公司 Air-conditioner system
WO2020202553A1 (en) * 2019-04-05 2020-10-08 三菱電機株式会社 Refrigeration cycle apparatus
US20220214081A1 (en) * 2019-07-22 2022-07-07 Mitsubishi Electric Corporation Air conditioning apparatus and outdoor unit

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58135667U (en) * 1982-03-08 1983-09-12 松下冷機株式会社 refrigeration cycle
JPH05332641A (en) 1992-05-29 1993-12-14 Daikin Ind Ltd Freezer device
JPH06213518A (en) 1993-01-13 1994-08-02 Hitachi Ltd Heat pump type air conditioner for mixed refrigerant
JP2003194432A (en) * 2001-10-19 2003-07-09 Matsushita Electric Ind Co Ltd Refrigerating cycle device

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3505789A1 (en) * 1985-02-20 1986-08-21 Grote, Paul, 2901 Friedrichsfehn SPIRAL HEAT EXCHANGER
JPH1054616A (en) * 1996-08-14 1998-02-24 Daikin Ind Ltd Air conditioner
TW568254U (en) * 1997-01-06 2003-12-21 Mitsubishi Electric Corp Refrigerant circulating apparatus
JPH11325655A (en) * 1998-05-14 1999-11-26 Matsushita Seiko Co Ltd Silencer and air conditioner
JP2001056188A (en) * 1999-06-10 2001-02-27 Sanden Corp Heat exchanger used in vapor pressurizing type refrigeration cycle and the like
KR100544323B1 (en) * 2000-04-28 2006-01-23 다이킨 고교 가부시키가이샤 Refrigerant and oil collection operating method and refrigerant and oil collection control device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58135667U (en) * 1982-03-08 1983-09-12 松下冷機株式会社 refrigeration cycle
JPH05332641A (en) 1992-05-29 1993-12-14 Daikin Ind Ltd Freezer device
JPH06213518A (en) 1993-01-13 1994-08-02 Hitachi Ltd Heat pump type air conditioner for mixed refrigerant
JP2003194432A (en) * 2001-10-19 2003-07-09 Matsushita Electric Ind Co Ltd Refrigerating cycle device

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP1944562A4 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10597446B2 (en) 2013-09-13 2020-03-24 Genentech, Inc. Method of treatment comprising purified recombinant IL-13 antibody

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CN101268312B (en) 2010-05-19
CN101268312A (en) 2008-09-17
JP2007085647A (en) 2007-04-05
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KR20080042178A (en) 2008-05-14
EP1944562A4 (en) 2011-03-23

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