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JP2007187420A - Air conditioner - Google Patents

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Publication number
JP2007187420A
JP2007187420A JP2006007578A JP2006007578A JP2007187420A JP 2007187420 A JP2007187420 A JP 2007187420A JP 2006007578 A JP2006007578 A JP 2006007578A JP 2006007578 A JP2006007578 A JP 2006007578A JP 2007187420 A JP2007187420 A JP 2007187420A
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Japan
Prior art keywords
heat exchanger
refrigerant
path
paths
air conditioner
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JP2006007578A
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Japanese (ja)
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JP4120680B2 (en
Inventor
Makoto Kojima
誠 小島
Takayuki Setoguchi
隆之 瀬戸口
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Daikin Industries Ltd
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Daikin Industries Ltd
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Priority to JP2006007578A priority Critical patent/JP4120680B2/en
Priority to CN2006101567452A priority patent/CN101149097B/en
Priority to KR1020087013407A priority patent/KR100973916B1/en
Priority to US12/087,100 priority patent/US20090025420A1/en
Priority to CN2007800017227A priority patent/CN101360961B/en
Priority to AU2007205443A priority patent/AU2007205443B2/en
Priority to EP07706803.9A priority patent/EP1975525A4/en
Priority to PCT/JP2007/050476 priority patent/WO2007081021A1/en
Publication of JP2007187420A publication Critical patent/JP2007187420A/en
Application granted granted Critical
Publication of JP4120680B2 publication Critical patent/JP4120680B2/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2507—Flow-diverting valves

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

【課題】複数のパスを有する空気調和機用熱交換器に対応する分流器の各パス間の冷媒の偏流を逆に適切に制御し、熱交換性能を向上させた空気調和機を提供する。
【解決手段】圧縮機と、四方弁と、室外熱交換器と、絞り装置と、複数のパスを有する室内熱交換器とからなり、これらを冷媒配管により順次接続して冷媒回路を構成するとともに、複数のパスを備えた室内熱交換器と絞り装置との間に複数のパスを備えた分流器を配設してなる空気調和機において、分流器の複数のパスの各々に冷媒流量調整弁を設け、その内の所定の運転状態において処理する能力が大きく室内熱交換器の出口側冷媒温度が高くなる所定のパスに対して、より多くの冷媒を配分するようにした。パスの管内流速は速くなり、また吸込み温度との温度差が広がるため、室内熱交換器の能力は向上し、冷凍能力がアップする。
【選択図】 図２An air conditioner having improved heat exchange performance by appropriately controlling the flow of refrigerant between the paths of a flow divider corresponding to a heat exchanger for an air conditioner having a plurality of paths.
A compressor, a four-way valve, an outdoor heat exchanger, a throttling device, and an indoor heat exchanger having a plurality of paths are sequentially connected by a refrigerant pipe to form a refrigerant circuit. An air conditioner in which a flow divider having a plurality of paths is disposed between an indoor heat exchanger having a plurality of paths and a throttle device, and a refrigerant flow rate adjusting valve is provided in each of the plurality of paths of the flow divider Among them, more refrigerant is distributed to a predetermined path that has a large capacity for processing in a predetermined operation state and the outlet side refrigerant temperature of the indoor heat exchanger becomes high. Since the flow velocity in the pipe of the pass increases and the temperature difference with the suction temperature widens, the capacity of the indoor heat exchanger is improved and the refrigeration capacity is increased.
[Selection] Figure 2

Description

本願発明は、空気調和機に関し、特に同空気調和機の室内熱交換器の複数のパスに適切に冷媒を分流させる分流器を備えた空気調和機の構成に関するものである。   The present invention relates to an air conditioner, and more particularly to a configuration of an air conditioner including a flow divider that appropriately diverts a refrigerant to a plurality of paths of an indoor heat exchanger of the air conditioner.

今例えば図５には、クロスフローファン２９を採用した一般的な壁掛け型の空気調和機（室内機）２１の構成を示している。   Now, for example, FIG. 5 shows a configuration of a general wall-mounted air conditioner (indoor unit) 21 that employs the cross flow fan 29.

同図５中において、符号２０は当該空気調和機２１の本体ケーシングであり、その上面側と正面側上部には、それぞれ第１，第２の２つの空気吸込グリル２３、２４が形成されている一方、正面側下方のコーナ部には空気吹出口２５が設けられている。   In FIG. 5, reference numeral 20 denotes a body casing of the air conditioner 21, and first and second air suction grilles 23 and 24 are formed on the upper surface side and the front side upper portion, respectively. On the other hand, an air outlet 25 is provided at a corner portion below the front side.

また、上記本体ケーシング２０内には上記各空気吸込グリル２３、２４から上記空気吹出口２５方向への送風通路２７が設けられており、この送風通路２７の上流領域には上記第１，第２の空気吸込グリル２３、２４の各面に対向した断面くの字形の室内熱交換器（ラムダ形熱交換器）２６が、その下流領域にはクロスフローファン２９、舌部２２およびスクロール部３０が順に併設されている。そして、上記舌部２２とスクロール部３０とによって、うず巻状のファンハウジングが形成され、それらの開口部３０ａ，２２ａ内には、クロスフローファン２９の羽根車（ファンロータ）２９ａが矢印方向に回転するように設置されている。   Further, a blower passage 27 is provided in the main body casing 20 from the air suction grilles 23 and 24 toward the air outlet 25, and the first and second areas in the upstream region of the blower passage 27 are provided. A cross-sectionally-shaped indoor heat exchanger (lambda-type heat exchanger) 26 facing each surface of the air suction grilles 23, 24, and a cross flow fan 29, tongue portion 22 and scroll portion 30 in the downstream region thereof. They are attached in order. The tongue portion 22 and the scroll portion 30 form a spiral fan housing, and an impeller (fan rotor) 29a of the cross flow fan 29 is formed in the direction of the arrow in the openings 30a and 22a. It is installed to rotate.

上記舌部２２は、上記第２の空気吸込グリル２４側に位置して上記クロスフローファン２９の羽根車（ファンロータ）２９ａの外径に沿って所定の高さを有して設けられている。   The tongue portion 22 is located on the second air suction grille 24 side and is provided with a predetermined height along the outer diameter of the impeller (fan rotor) 29a of the crossflow fan 29. .

そして、その下部側は上記室内熱交換器２６下方のドレンパンと兼用された空気流ガイド部２２ｂに連続している。そして、この空気流ガイド部２２ｂは、上記クロスフローファン２９の羽根車（ファンロータ）２９ａから吹き出された空気流が効率よく上記空気吹出口２５から吹き出されるように、その下流側は上記スクロール部３０の下流側部分３０ｂと共に上記空気吹出口２５方向に向けて図示のようなディフューザー構造の空気吹出通路２８を形成している。   And the lower part side is following the air flow guide part 22b used also as the drain pan of the said indoor heat exchanger 26 lower part. The air flow guide portion 22b is arranged on the downstream side so that the air flow blown out from the impeller (fan rotor) 29a of the cross flow fan 29 is blown out from the air blowout port 25 efficiently. An air outlet passage 28 having a diffuser structure as illustrated is formed in the direction of the air outlet 25 together with the downstream portion 30b of the portion 30.

なお、符号３１は、上記スクロール部３０と上記舌部２２下部の空気流ガイド部２２ｂとの間のディフューザ構造の空気吹出通路２８内に設けられた風向変更板である。   Reference numeral 31 denotes a wind direction changing plate provided in the air blowing passage 28 of the diffuser structure between the scroll portion 30 and the air flow guide portion 22b below the tongue portion 22.

そして、上記舌部２２の形状は、図示のように形成されており、上記室内熱交換器２６を経て上記クロスフローファン２９の羽根車（ファンロータ）２９ａから上記空気吹出口２５に到る空気の流れは、鎖線矢印で示すように全体として回転方向に湾曲しながら羽根車（ファンロータ）２９ａの回転軸と直交方向に貫流して吹き出され、その後、上記空気吹出通路２８に沿って上記空気吹出口２５方向に曲げられて前面側に吹き出される。   The shape of the tongue 22 is formed as shown in the figure, and the air reaching the air outlet 25 from the impeller (fan rotor) 29a of the crossflow fan 29 via the indoor heat exchanger 26 is formed. As shown by a chain line arrow, the flow of the air flows in a direction orthogonal to the rotation axis of the impeller (fan rotor) 29a while being curved in the rotational direction as a whole, and then blown out along the air blowing passage 28. It is bent in the direction of the air outlet 25 and blown out to the front side.

このような構成の空気調和機用の室内熱交換器２６の場合、例えば図示Ａ部、Ｂ部、Ｃ部、Ｄ部に区分して、低負荷時の風速分布を分析して見ると、正面側第２の空気吸込グリル２４に真正面に対応するＤ部の風速が最も高く、上面側第１の空気吸込グリル２３に対応してはいるが、対応状態が斜目になるＣ部では上記Ｄ部より少し低下し、また本体ケーシング２０の前面側上部の一部によって覆われ、ストレートには空気が流入しないＢ部では、上記Ｃ部よりも風速が低下する。さらに、上述の舌部２２によって空気が遮ぎられるＡ部では、上記Ｂ部よりもさらに風速が低下する。   In the case of the indoor heat exchanger 26 for an air conditioner having such a configuration, for example, when divided into an A part, a B part, a C part, and a D part shown in the drawing, the wind speed distribution at low load is analyzed and viewed, The portion D corresponding to the front side of the second air suction grille 24 has the highest wind speed and corresponds to the first air suction grille 23 on the upper surface side, but in the portion C where the corresponding state is oblique, the above D In part B, which is slightly lower than the part and is covered by a part of the upper part on the front side of the main body casing 20 and air does not flow straight, the wind speed is lower than that in part C. Furthermore, in the A portion where the air is blocked by the tongue portion 22 described above, the wind speed is further lowered than in the B portion.

そして、上記のような空気調和機の複数のパスを有する室内熱交換器２６では、当該室内熱交換器２６本体に流入する冷媒を当該室内熱交換器２６本体の各パスに分配するために、一般に図６のような複数の分流パス７ａ，７ｂを有する分流器６を設けており、同分流器６では、定格運転時に合わせて各分流パス７ａ，７ｂの冷媒の分配比を決めている。   And in the indoor heat exchanger 26 having a plurality of paths of the air conditioner as described above, in order to distribute the refrigerant flowing into the indoor heat exchanger 26 main body to each path of the indoor heat exchanger 26 main body, Generally, a flow divider 6 having a plurality of flow dividing paths 7a and 7b as shown in FIG. 6 is provided. In the flow divider 6, the distribution ratio of the refrigerant in each flow dividing path 7a and 7b is determined in accordance with the rated operation.

なお、Ｖは分流器６の入口側の膨張弁、６ａは分流器６の冷媒流入口である。   V is an expansion valve on the inlet side of the flow divider 6, and 6 a is a refrigerant inlet of the flow divider 6.

したがって、定格運転時には室内熱交換器２６の出口側各パス８Ａ，８Ｂの出口側冷媒温度はほぼ等しくなる（図６中に矢線の太さで表現）。しかし、一方冷媒量が少なくなる低負荷（部分負荷）時になると、上記のように室内熱交換器２６の送風通路位置に応じて異なる風速分布の影響により、例えば図７のグラフに示すように、風速が速いパス７ａ，８Ａ（白地で表示）の冷媒は熱交換容量に余裕があるために出口側温度が高くなる一方、逆に風速の遅いパス７ｂ，８Ｂ（ドット地で表示）の冷媒は、熱交換容量に余裕がなくなるために、同冷媒の出口側温度はそれよりも低くなる問題が生じる（図７のΔＴ参照）。   Therefore, at the rated operation, the outlet side refrigerant temperatures of the outlet side paths 8A and 8B of the indoor heat exchanger 26 are substantially equal (represented by the thickness of the arrow in FIG. 6). However, at the time of low load (partial load) when the amount of refrigerant decreases, due to the influence of the wind speed distribution that differs depending on the air passage position of the indoor heat exchanger 26 as described above, for example, as shown in the graph of FIG. The refrigerant in the paths 7a and 8A (indicated by white background) with the fast wind speed has a high heat exchange capacity, so the outlet side temperature becomes high. On the other hand, the refrigerant in the paths 7b and 8B (indicated by dot background) in which the wind speed is slow is Since there is no room for the heat exchange capacity, there arises a problem that the outlet side temperature of the refrigerant becomes lower (see ΔT in FIG. 7).

そこで、このような問題を解決する方法の一つとして、従来例では、例えば図８に示すように、少なくとも低負荷時において出口側温度が低下するパス７ｂ，８Ｂに冷媒流量調整弁Ｖ1を設けて相対的に流量を調節することにより、例えば図９のグラフ（風速の遅い方をドット地で表示）に示すように、各パス７ａ，８Ａと７ｂ，８Ｂの出口側温度（乾き度）を合わせる方法を採用している（例えば特許文献１参照）。 Therefore, as one method for solving such a problem, in the conventional example, as shown in FIG. 8, for example, the refrigerant flow rate adjustment valve V 1 is provided in the paths 7b and 8B where the outlet side temperature decreases at least at the time of low load. By providing and relatively adjusting the flow rate, for example, as shown in the graph of FIG. 9 (in which the slower wind speed is indicated by a dot area), the outlet side temperatures (dryness) of the paths 7a, 8A and 7b, 8B are shown. Is used (see, for example, Patent Document 1).

特開平５−１１８６８２号公報（明細書第１〜第３頁、図１−２）Japanese Patent Laid-Open No. 5-118682 (Specifications, first to third pages, FIG. 1-2)

しかし、このような構成では、特に乾き度（図中にシャドウ度合を高くして濃く表示）が高いような場合、上記低負荷時における能力はそれほど向上しない。   However, with such a configuration, particularly when the dryness (indicated by darkness with a high shadow degree in the drawing) is high, the capability at the time of low load is not improved so much.

本願発明は、複数のパスを有する空気調和機用熱交換器に対応する分流器の各パス間の冷媒の偏流を逆に適切に制御し、熱交換性能を向上させた空気調和機を提供することを目的とするものである。   The present invention provides an air conditioner with improved heat exchange performance by appropriately controlling the reverse flow of refrigerant between each path of a flow divider corresponding to a heat exchanger for an air conditioner having a plurality of paths. It is for the purpose.

本願発明は、上記の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。   In order to achieve the above object, the present invention is configured with the following problem solving means.

（１） 第１の課題解決手段
この発明の第１の課題解決手段は、圧縮機と、四方弁と、室外熱交換器と、絞り装置と、複数のパスを有する室内熱交換器とからなり、これらを冷媒配管により順次接続して冷媒回路を構成するとともに、上記複数のパスを備えた室内熱交換器と絞り装置との間に上記複数のパスを備えた分流器を配設してなる空気調和機において、上記分流器の複数のパスの各々に冷媒流量調整弁を設け、その内の所定の運転状態において処理する能力が大きく上記室内熱交換器の出口側冷媒温度が高くなる所定のパスに対して、より多くの冷媒を配分するようにしたことを特徴としている。 (1) First problem solving means The first problem solving means of the present invention comprises a compressor, a four-way valve, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger having a plurality of paths. These are sequentially connected by refrigerant piping to form a refrigerant circuit, and a flow divider having the plurality of paths is disposed between the indoor heat exchanger having the plurality of paths and the expansion device. In the air conditioner, a refrigerant flow rate adjustment valve is provided in each of the plurality of paths of the flow divider, and the ability to process in a predetermined operation state is large, and the outlet side refrigerant temperature of the indoor heat exchanger is high. It is characterized in that more refrigerant is distributed to the path.

このように、所定の運転状態において、処理する能力に余裕のあるパスに対して、積極的に冷媒をより多く配分するようにすると、当該パスの管内流速は速くなり、また吸込み温度との温度差が広がるため、室内熱交換器の能力は有効に向上し、冷凍能力がアップする。   In this way, if a larger amount of refrigerant is positively distributed to a path with sufficient capacity for processing in a predetermined operating state, the flow velocity in the pipe of the path increases, and the temperature with respect to the suction temperature. Since the difference widens, the capacity of the indoor heat exchanger is effectively improved and the refrigeration capacity is increased.

（２） 第２の課題解決手段
この発明の第２の課題解決手段は、上記第１の課題解決手段の構成において、所定の運転状態が低負荷時であり、該低負荷時には、処理する能力が小さく室内熱交換器の出口側冷媒温度が低くなる所定のパスの冷媒流量調整弁を絞り、処理する能力が大きく上記室内熱交換器の出口側冷媒温度が高くなるパスに多くの冷媒を流すようにしたことを特徴としている。 (2) Second Problem Solving Means According to a second problem solving means of the present invention, in the configuration of the first problem solving means, the predetermined operation state is at a low load, and the processing capability is at the low load. The refrigerant flow rate adjustment valve of a predetermined path where the outlet side refrigerant temperature of the indoor heat exchanger is low is throttled, and a large amount of refrigerant flows through the path where the processing capacity is large and the outlet side refrigerant temperature of the indoor heat exchanger is high It is characterized by doing so.

このように、全体の冷媒流量が少なくなる低負荷時においては、処理する能力が小さく室内熱交換器の出口側冷媒温度が低くなる所定のパスの冷媒流量調整弁を絞り、他方処理する能力に余裕のある風速の速いパスに冷媒をより多く配分するようにすると、当該パスの管内流速は速くなり、また吸込み温度との温度差が広がるため、有効に熱交換器の能力が向上し、冷凍能力がアップする。   In this way, at low loads where the overall refrigerant flow rate is low, the ability to process is small, and the refrigerant flow rate adjustment valve in a predetermined path where the outlet side refrigerant temperature of the indoor heat exchanger is low is throttled, and the other is capable of processing. If more refrigerant is distributed to a path with sufficient wind speed, the flow velocity in the pipe in the path increases, and the temperature difference from the suction temperature increases, effectively improving the capacity of the heat exchanger and reducing the refrigeration. Ability improves.

（３） 第３の課題解決手段
この発明の第３の課題解決手段は、上記第１の課題解決手段の構成において、所定のパスが風速の遅いパスであり、低負荷時には該風速の遅いパスの冷媒流量調整弁を絞り、熱交換能力に余裕のある風速の速い部分を流れるパスにより多くの冷媒を流すようにしたことを特徴としている。 (3) Third Problem Solving Means According to a third problem solving means of the present invention, in the configuration of the first problem solving means, the predetermined path is a path with a slow wind speed, and when the load is low, the path with the slow wind speed is provided. The refrigerant flow rate adjusting valve is throttled so that a larger amount of refrigerant flows through a path that flows through a portion with a high wind speed that has a sufficient heat exchange capacity.

このように、全体の冷媒流量が少なくなる低負荷時において、処理する能力に余裕のない風速の遅いパスの冷媒流量調整弁を絞り、他方熱交換能力に余裕のある風速の速い部分を流れるパスに冷媒をより多く配分するようにすると、当該パスの管内流速は速くなり、また吸込み温度との温度差が広がるため、有効に熱交換器の能力が向上し、冷凍能力がアップする。   In this way, at low load when the overall refrigerant flow rate is low, the refrigerant flow rate adjustment valve in the slow wind speed path that has no capacity to handle is throttled, while the path that flows through the fast wind speed section that has sufficient heat exchange capacity If more refrigerant is distributed to the pipe, the flow velocity in the pipe of the path increases, and the temperature difference from the suction temperature widens, so that the capacity of the heat exchanger is effectively improved and the refrigeration capacity is increased.

（４） 第４の課題解決手段
この発明の第４の課題解決手段は、上記第１の課題解決手段の構成において、所定の運転状態が定格負荷時であり、該定格負荷時には、各パスの冷媒流量調整弁を全開として、熱交換器の能力をフルに発揮させるようにしたことを特徴としている。 (4) Fourth Problem Solving Means According to a fourth problem solving means of the present invention, in the configuration of the first problem solving means, the predetermined operation state is at the rated load, and at the rated load, The refrigerant flow rate adjusting valve is fully opened, and the heat exchanger capacity is fully exhibited.

このように、定格運転状態においては、各パスの冷媒流量調整弁を全開として、熱交換器の能力をフルに発揮させる。   In this way, in the rated operation state, the refrigerant flow rate adjustment valve of each path is fully opened, and the heat exchanger capacity is fully exhibited.

以上の結果、本願発明によると、単に室内熱交換器の各パスの出口側温度を等しくするだけの従来の構成に比べて、空気調和機用熱交換器の熱交換能力をより有効に向上させることができる。   As a result of the above, according to the present invention, the heat exchange capacity of the air conditioner heat exchanger is more effectively improved as compared with the conventional configuration in which the outlet side temperatures of the respective paths of the indoor heat exchanger are simply made equal. be able to.

（最良の実施の形態１）
図１〜図２は、本願発明の最良の実施の形態１に係る空気調和機の冷凍回路およびその分流器部分の構成を、また図３は、その作用効果を示している。この実施の形態の構成では、説明を簡単にするために、図５の熱交換器２６部分の風速域を低風速部Ａ，Ｂと高風速部Ｃ，Ｄの２つの領域に大別し、それに対応して分流器６部分のパス数が２つの場合について例示している。 (Best Embodiment 1)
1 to 2 show the configuration of the refrigeration circuit of the air conditioner and its shunt portion according to the best embodiment 1 of the present invention, and FIG. 3 shows the function and effect thereof. In the configuration of this embodiment, in order to simplify the description, the wind speed region of the heat exchanger 26 portion of FIG. 5 is roughly divided into two regions, a low wind speed portion A, B and a high wind speed portion C, D. Correspondingly, the case where the number of paths of the shunt 6 is two is illustrated.

先ず図１において、１は室外機、２は圧縮機、３は四方弁、４は室外熱交換器、５は絞り装置、６は分流器、６ａは分流器６への冷媒流入口、７ａは分流器６の第１の分流パス、７ｂは同分流器６の第２の分流パス、２６は室内熱交換器、８Ａは室内熱交換器２６の出口側第１のパス、８Ｂは同室内熱交換器２６の出口側第２のパス、１０は室内機、Ｖは膨張弁であり、これらを第１の冷媒配管９Ａ、第２の冷媒配管９Ｂにより接続して、図示のような可逆的な冷媒循環回路を構成している。   First, in FIG. 1, 1 is an outdoor unit, 2 is a compressor, 3 is a four-way valve, 4 is an outdoor heat exchanger, 5 is a throttling device, 6 is a flow divider, 6a is a refrigerant inlet to the flow divider 6, 7a is The first shunt path of the shunt 6, 7 b is the second shunt path of the shunt 6, 26 is the indoor heat exchanger, 8 A is the first path on the outlet side of the indoor heat exchanger 26, and 8 B is the same room heat. The second path on the outlet side of the exchanger 26 is an indoor unit, V is an expansion valve, and these are connected by a first refrigerant pipe 9A and a second refrigerant pipe 9B so as to be reversible as shown in the figure. A refrigerant circulation circuit is configured.

そして、上記室内熱交換器２６と絞り装置５との間に上記膨張弁Ｖおよび分流器６を配設している。分流器６の第１，第２の分流パス７ａ，７ｂには、それぞれ電気的に開度調整可能な電磁弁よりなる第１，第２の冷媒流量調整弁Ｖ1，Ｖ2を設け、所定の運転状態において、処理する能力が大きく熱交換器８の出口側の冷媒温度が高くなる所定のパス７ａ又は７ｂの何れか一方に冷媒をより多く配分するようにしている。この冷媒配分量の制御は、例えばマイコンを備えた所定の制御ユニットにより、上記第１，第２の冷媒流量調整弁Ｖ1，Ｖ2の開度を個別に制御することによってなされる。 The expansion valve V and the flow divider 6 are disposed between the indoor heat exchanger 26 and the expansion device 5. The first and second diversion paths 7a and 7b of the flow divider 6 are respectively provided with first and second refrigerant flow rate adjustment valves V 1 and V 2 made of electromagnetic valves whose opening degree can be adjusted electrically. In this operating state, a larger amount of refrigerant is distributed to either one of the predetermined paths 7a or 7b where the processing capacity is large and the refrigerant temperature on the outlet side of the heat exchanger 8 is high. The refrigerant distribution amount is controlled by individually controlling the opening degrees of the first and second refrigerant flow rate adjusting valves V 1 and V 2 by, for example, a predetermined control unit including a microcomputer.

この場合、上記所定の運転状態は、例えば分流器６の冷媒流入口６ａへの冷媒流量が少なくなる低負荷時であり、例えば図２に示すように、同低負荷時において第２の分流パス７ｂ側の風速が遅く、第１の分流パス７ａ側の風速が速いとすると、同低負荷時には、例えば熱交換能力に余裕のない風速の遅い第２の分流パス７ｂの方の冷媒流量調整弁Ｖ2の弁開度を絞る一方、熱交能力に余裕のある他方側の風速の速い第１の分流パス７ａの方により多くの冷媒を流すように制御している。 In this case, the predetermined operating state is, for example, at low load when the refrigerant flow rate to the refrigerant inlet 6a of the flow divider 6 is small. For example, as shown in FIG. If the wind speed on the 7b side is slow and the wind speed on the first shunt path 7a is fast, at the same low load, for example, the refrigerant flow rate adjusting valve on the second shunt path 7b with a slow wind speed with no margin for heat exchange capacity, for example. While the valve opening degree of V 2 is reduced, control is performed so that more refrigerant flows through the first diversion path 7a on the other side having a sufficient heat exchange capability and having a fast wind speed.

このように全体の冷媒流量が少なくなる低負荷時において、処理する能力に余裕のない風速の遅い第２の分流パス７ｂの冷媒流量調整弁Ｖ2を絞り、逆に処理する能力に余裕のある風速の速い第１の分流パス７ａの方に冷媒をより多く配分するようにすると、同風速の速い第１の分流パス７ａの管内流速は速くなり、また図３のグラフ（第１の分流パス７ａ側を白地、第２の分流パス７ｂ側をドット地で表示）に示すように吸込み温度との温度差ΔＴが広がるため、室内熱交換器２６の能力は向上し、冷凍能力がアップする。 In this way, at the time of a low load where the entire refrigerant flow rate is reduced, the refrigerant flow rate adjustment valve V2 of the second shunt path 7b having a slow wind speed without a sufficient processing capability is throttled, and there is a margin in the processing capability. If a larger amount of refrigerant is distributed toward the first diversion path 7a having a higher wind speed, the pipe flow velocity of the first diversion path 7a having the same wind speed is increased, and the graph of FIG. Since the temperature difference ΔT with respect to the suction temperature is widened as shown by white background on the 7a side and dot ground on the second diversion path 7b side), the capacity of the indoor heat exchanger 26 is improved and the refrigeration capacity is increased.

一方、定格負荷時には、上記第１，第２の冷媒流量調整弁Ｖ1，Ｖ2を全開として、上記室内熱交換器２６の熱交換能力をフルに発揮させる。 On the other hand, at the rated load, the first and second refrigerant flow rate adjusting valves V 1 and V 2 are fully opened, and the heat exchange capability of the indoor heat exchanger 26 is fully exhibited.

以上の結果、本実施の形態によると、単に室内熱交換器２６の各パス８Ａ，８Ｂの出口側温度を等しくするだけの従来の構成に比べて、空気調和機用室内熱交換器２６の熱交換能力をより有効に向上させることができる。   As a result of the above, according to the present embodiment, the heat of the indoor heat exchanger 26 for the air conditioner can be compared with the conventional configuration in which the outlet side temperatures of the paths 8A and 8B of the indoor heat exchanger 26 are simply made equal. The exchange capacity can be improved more effectively.

（最良の実施の形態２）
次に図４は、本願発明の最良の実施の形態２に係る空気調和機の分流器および室内熱交換器部分の構成を示している。 (Best Mode 2)
Next, FIG. 4 shows the configuration of the shunt and the indoor heat exchanger portion of the air conditioner according to the second preferred embodiment of the present invention.

上述の最良の実施の形態１の構成では、説明を分り易くするために、例えば図６の室内熱交換器２６の風速分布域を低風速部Ａ，Ｂと高風速部Ｃ，Ｄの２つの風速域に大別して第１，第２の２つの分流パス７ａ，７ｂに分流させる場合について説明したが、この最良の実施の形態２の構成では、同図６の熱交換器２６の風速域を、例えば低風速域Ａ部，Ｂ部、Ｃ部と高風速部Ｄ部の４つの風速域に細かく分け、それぞれの部分に対応して第１，第２，第３，第４の分流パス７ａ〜７ｄを設け、それらの各々に上述の場合と同様の第１〜第４の冷媒流量調整弁Ｖ21〜Ｖ24を設けたことを特徴とするものである。 In the configuration of the first embodiment described above, for the sake of easy understanding, for example, the wind speed distribution area of the indoor heat exchanger 26 in FIG. 6 is divided into two wind speed sections A and B and high wind speed sections C and D. Although the description has been given of the case where the flow is divided roughly into the first and second diversion paths 7a and 7b, the wind speed range of the heat exchanger 26 in FIG. For example, the wind speed regions A, B, C, and the high wind speed portion D are subdivided into four wind speed regions, and the first, second, third, and fourth shunt paths 7a corresponding to the respective portions. ˜7d are provided, and the first to fourth refrigerant flow rate adjustment valves V 21 to V 24 similar to those described above are provided for each of them.

このように、第１〜第４の分流パス７ａ〜７ｄを有する場合においても、少なくとも全体の冷媒流量が少なくなる低負荷時においては、処理する能力に余裕のない風速の遅い第１〜第３の分流パス７ａ〜７ｃの第１〜第３の冷媒流量調整弁Ｖ21〜Ｖ23を絞り、処理する能力に余裕のある風速の速い第４の分流パス７ｄの方に冷媒をより多く配分するようにすると、当該第４の分流パス７ｄの管内流速は速くなり、また吸込み温度との温度差が広がるため、室内熱交換器２６の能力は向上し、冷凍能力がアップする。 Thus, even in the case of having the first to fourth diversion paths 7a to 7d, at least at the time of low load where the entire refrigerant flow rate is reduced, the first to third slow wind speeds with no margin for processing ability. to allocate more coolant towards the aperture first to third refrigerant flow rate control valve V 21 ~V 23 of the shunt path 7 a to 7 c, processing fast wind speed with spare capacity to the fourth shunt path 7d By doing so, the flow velocity in the pipe of the fourth diversion path 7d is increased and the temperature difference from the suction temperature is widened, so that the capacity of the indoor heat exchanger 26 is improved and the refrigeration capacity is increased.

他方、定格負荷時には、上記第１〜第４の分流パス７ａ〜７ｄの各冷媒流量調整弁Ｖ21〜Ｖ24をそれぞれ全開として、室内熱交換器２６の能力をフルに発揮させる。 On the other hand, at the rated load, the refrigerant flow rate adjustment valves V 21 to V 24 of the first to fourth diversion paths 7 a to 7 d are fully opened, so that the capacity of the indoor heat exchanger 26 is fully exhibited.

本願発明の最良の実施の形態１に係る空気調和機の冷凍回路図である。1 is a refrigeration circuit diagram of an air conditioner according to Embodiment 1 of the present invention. 同空気調和機の室内機の複数のパスを備えた熱交換器と該熱交換器各パスに対応した分流器の構成と作用を示す図である。It is a figure which shows the structure and effect | action of a heat exchanger provided with the several path | pass of the indoor unit of the air conditioner, and the shunt corresponding to each path | pass of this heat exchanger. 同空気調和機の図２の分流器による室内熱交換器の定格時と低負荷時の出口温度を対比して示す図である。It is a figure which compares and shows the outlet temperature at the time of the rating of the indoor heat exchanger by the shunt of FIG. 2 of the same air conditioner, and low load. 本願発明の最良の実施の形態２に係る空気調和機の室内機の複数のパスを備えた熱交換器と該熱交換器各パスに対応した分流器の構成を示す図である。It is a figure which shows the structure of the heat exchanger provided with the several path | pass of the indoor unit of the air conditioner which concerns on the best Embodiment 2 of this invention, and the shunt corresponding to each path | pass of this heat exchanger. 従来一般の空気調和機の室内機の構成を示す図である。It is a figure which shows the structure of the indoor unit of the conventional general air conditioner. 同従来一般の空気調和機の室内機の複数のパスを備えた熱交換器と該熱交換器に対応した分流器の構成と作用を示す図である。It is a figure which shows the structure and effect | action of a heat exchanger provided with the several path | pass of the indoor unit of the conventional general air conditioner, and the shunt corresponding to this heat exchanger. 同従来一般の空気調和機の図６の分流器による室内熱交換器の定格時と低負荷時の出口温度を対比して示す図である。It is a figure which compares and shows the outlet temperature at the time of the rating of the indoor heat exchanger by the shunt of FIG. 6 of the conventional general air conditioner, and the time of low load. 出口温度対策を施した従来例に係る空気調和機の室内機の複数のパスを備えた熱交換器と該熱交換器に対応した分流器の構成と作用を示す図である。It is a figure which shows the structure and effect | action of a heat exchanger provided with the several path | pass of the indoor unit of the air conditioner which concerns on the prior art example which took the exit temperature countermeasure, and a shunt corresponding to this heat exchanger. 同従来例に係る空気調和機の図８の分流器による室内熱交換器の定格時と低負荷時の出口温度を対比して示す図である。It is a figure which compares and shows the outlet temperature at the time of the rating of the indoor heat exchanger by the shunt of FIG. 8 of the air conditioner which concerns on the prior art example, and low load.

符号の説明Explanation of symbols

１は室外機、２は圧縮機、３は四方弁、４は室外熱交換器、５は絞り装置、６は分流器、６ａは分流器６への冷媒流入口、７ａは分流器６の第１の分流パス、７ｂは同分流器６の第２の分流パス、８Ａは熱交換器２６の出口側第１のパス、８Ｂは同熱交換器２６の出口側第２のパス、１０は室内機、２６は室内熱交換器、Ｖは膨張弁、Ｖ1は第１の冷媒流量調整弁、Ｖ2は第２の流量調整弁である。 1 is an outdoor unit, 2 is a compressor, 3 is a four-way valve, 4 is an outdoor heat exchanger, 5 is a throttling device, 6 is a flow divider, 6a is a refrigerant inlet to the flow divider 6, and 7a is the first of the flow divider 6. 1B is a second diversion path of the flow divider 6, 8A is a first path on the outlet side of the heat exchanger 26, 8B is a second path on the outlet side of the heat exchanger 26, and 10 is a room. , 26 is an indoor heat exchanger, V is an expansion valve, V 1 is a first refrigerant flow control valve, and V 2 is a second flow control valve.

Claims (4)

圧縮機と、四方弁と、室外熱交換器と、絞り装置と、複数のパスを有する室内熱交換器とからなり、これらを冷媒配管により順次接続して冷媒回路を構成するとともに、上記複数のパスを備えた室内熱交換器と絞り装置との間に上記複数のパスを備えた分流器を配設してなる空気調和機において、上記分流器の複数のパスの各々に冷媒流量調整弁を設け、その内の所定の運転状態において処理する能力が大きく上記室内熱交換器の出口側冷媒温度が高くなる所定のパスに対して、より多くの冷媒を配分するようにしたことを特徴とする空気調和機。   It consists of a compressor, a four-way valve, an outdoor heat exchanger, an expansion device, and an indoor heat exchanger having a plurality of paths, which are sequentially connected by a refrigerant pipe to constitute a refrigerant circuit, and An air conditioner comprising a flow divider having a plurality of paths disposed between an indoor heat exchanger having a path and a throttle device, wherein a refrigerant flow rate adjusting valve is provided in each of the plurality of paths of the flow divider. It is characterized in that a larger amount of refrigerant is distributed to a predetermined path in which the capacity of processing in a predetermined operation state is large and the outlet side refrigerant temperature of the indoor heat exchanger is high. Air conditioner. 所定の運転状態が低負荷時であり、該低負荷時には、処理する能力が小さく室内熱交換器の出口側冷媒温度が低くなる所定のパスの冷媒流量調整弁を絞り、処理する能力が大きく上記室内熱交換器の出口側冷媒温度が高くなるパスに多くの冷媒を流すようにしたことを特徴とする請求項１記載の空気調和機。   The predetermined operating state is when the load is low, and when the load is low, the ability to process is small and the refrigerant flow rate adjustment valve in a predetermined path where the outlet side refrigerant temperature of the indoor heat exchanger is low is throttled and the ability to process is large. The air conditioner according to claim 1, wherein a large amount of refrigerant flows through a path in which the outlet side refrigerant temperature of the indoor heat exchanger increases. 所定のパスが風速の遅いパスであり、低負荷時には該風速の遅いパスの冷媒流量調整弁を絞り、熱交換能力に余裕のある風速の速い部分を流れるパスにより多くの冷媒を流すようにしたことを特徴とする請求項１記載の空気調和機。   The predetermined path is a path with a slow wind speed, and when the load is low, the refrigerant flow rate adjustment valve of the path with the slow wind speed is throttled so that more refrigerant flows through the path that flows through the fast wind speed portion with sufficient heat exchange capacity. The air conditioner according to claim 1. 所定の運転状態が定格負荷時であり、該定格負荷時には、各パスの冷媒流量調整弁を全開として、熱交換器の能力をフルに発揮させるようにしたことを特徴とする請求項１記載の空気調和機。
The predetermined operation state is at a rated load, and at the rated load, the refrigerant flow rate regulating valve of each path is fully opened to fully exhibit the capacity of the heat exchanger. Air conditioner.
JP2006007578A 2006-01-16 2006-01-16 Air conditioner Expired - Fee Related JP4120680B2 (en)

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JP2006007578A JP4120680B2 (en) 2006-01-16 2006-01-16 Air conditioner
CN2006101567452A CN101149097B (en) 2006-01-16 2006-12-28 Chain tensioner
US12/087,100 US20090025420A1 (en) 2006-01-16 2007-01-16 Air Conditioner
CN2007800017227A CN101360961B (en) 2006-01-16 2007-01-16 Air conditioner
KR1020087013407A KR100973916B1 (en) 2006-01-16 2007-01-16 Air conditioner
AU2007205443A AU2007205443B2 (en) 2006-01-16 2007-01-16 Air conditioner
EP07706803.9A EP1975525A4 (en) 2006-01-16 2007-01-16 AIR CONDITIONER
PCT/JP2007/050476 WO2007081021A1 (en) 2006-01-16 2007-01-16 Air conditioner

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