JP7444641B2 - refrigerant flow divider - Google Patents

refrigerant flow divider Download PDF

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JP7444641B2
JP7444641B2 JP2020036208A JP2020036208A JP7444641B2 JP 7444641 B2 JP7444641 B2 JP 7444641B2 JP 2020036208 A JP2020036208 A JP 2020036208A JP 2020036208 A JP2020036208 A JP 2020036208A JP 7444641 B2 JP7444641 B2 JP 7444641B2
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refrigerant
flow divider
stirring chamber
downstream end
branch
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JP2021139529A (en
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太照 岩成
恒星 酒井
康平 深渡瀬
博 鳥越
浩 濱本
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Japan Climate Systems Corp
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Japan Climate Systems Corp
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Priority to JP2020036208A priority Critical patent/JP7444641B2/en
Priority to EP21763817.0A priority patent/EP4102156B1/en
Priority to PCT/JP2021/007539 priority patent/WO2021177191A1/en
Priority to CN202180017778.1A priority patent/CN115210514B/en
Publication of JP2021139529A publication Critical patent/JP2021139529A/en
Priority to US17/898,597 priority patent/US20220412620A1/en
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    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/48—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow path resistance control on the downstream side of the diverging point, e.g. by an orifice
    • 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
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F25B41/45—Arrangements for diverging or converging flows, e.g. branch lines or junctions for flow control on the upstream side of the diverging point, e.g. with spiral structure for generating turbulence
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • 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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Description

本発明は、流入した冷媒を複数の流路に分流させる冷媒分流器に関する。 The present invention relates to a refrigerant flow divider that divides an inflowing refrigerant into a plurality of channels.

従来より、例えば冷凍サイクルの冷媒蒸発器として用いられる熱交換器が複数の伝熱管を備えている場合がある。この場合、流入管から流入した冷媒を各伝熱管に分流させるための冷媒分流器が用いられることがある（例えば、特許文献１参照）。 Conventionally, a heat exchanger used as a refrigerant evaporator in a refrigeration cycle, for example, may include a plurality of heat transfer tubes. In this case, a refrigerant flow divider may be used to divide the refrigerant flowing from the inflow pipe to each heat transfer tube (for example, see Patent Document 1).

特許文献１の冷媒分流器は、冷媒供給路及び絞り部が形成された第１の器体と、冷媒流衝突部及び第１、第２の分流路が形成された第２の器体とを互いに嵌合させて一体化することによって構成されている。冷媒供給路の下流端部の流路径を、テーパ面を介して縮小することによって絞り部が形成されている。一方、第２の器体の冷媒流衝突部は、冷媒供給路の下流端開口に対向するように配置されており、半球状の凹面で構成されている。第１、第２の分流路は、冷媒流衝突部の外方に開口している。そして、冷媒供給路を流れる冷媒は絞り部を通過してから冷媒流衝突部に衝突した後、第１、第２の分流路に分流して流れるようになっている。 The refrigerant flow divider of Patent Document 1 includes a first body in which a refrigerant supply path and a throttle portion are formed, and a second body in which a refrigerant flow collision portion and first and second flow dividers are formed. They are constructed by fitting them together and integrating them. The constricted portion is formed by reducing the flow path diameter at the downstream end of the refrigerant supply path via the tapered surface. On the other hand, the refrigerant flow collision part of the second vessel is disposed so as to face the downstream end opening of the refrigerant supply path, and has a hemispherical concave surface. The first and second branch channels are open to the outside of the refrigerant flow collision section. The refrigerant flowing through the refrigerant supply path passes through the throttle section, collides with the refrigerant flow collision section, and then branches into the first and second branch channels.

特開平１１－２５７８０１号公報Japanese Patent Application Publication No. 11-257801

ところで、特許文献１では、冷媒流衝突部が絞り部の開口に対向しているので、絞り部から流出する冷媒をまっすぐに流さなければ、冷媒を冷媒流衝突部に狙い通りに衝突させることができない構成となっている。 By the way, in Patent Document 1, since the refrigerant flow collision part faces the opening of the constriction part, unless the refrigerant flowing out from the constriction part flows straight, the refrigerant cannot collide with the refrigerant flow collision part as intended. The configuration is such that it is not possible.

ところが、絞り部は冷媒供給路の下流端部においてテーパ状に設けられているだけなので、絞り部の長さが短くなっており、絞り部によって冷媒の流出方向をコントロールすることは困難である。このため、絞り部に連通する配管を所定長さにわたって直管形状にしておき、この直管形状の部分により、冷媒が冷媒流衝突部に狙い通りに衝突するように冷媒の流出方向を設定しておく必要があった。直管形状の部分を所定長さ設けようとすると、冷媒分流器周辺の配管レイアウトが困難になる場合が考えられる。 However, since the constriction part is only provided in a tapered shape at the downstream end of the refrigerant supply path, the length of the constriction part is short, and it is difficult to control the outflow direction of the refrigerant using the constriction part. For this reason, the piping that communicates with the throttle section is made straight over a predetermined length, and the outflow direction of the refrigerant is set using this straight section so that the refrigerant collides with the refrigerant flow collision section as intended. I needed to keep it. If an attempt is made to provide a straight pipe-shaped portion with a predetermined length, the piping layout around the refrigerant flow divider may become difficult.

本発明は、かかる点に鑑みてなされたものであり、その目的とするところは、絞り部の上流に位置する配管の形状に依らず、狙い通りの冷媒分流を可能にすることにある。 The present invention has been made in view of this point, and its purpose is to enable targeted refrigerant diversion regardless of the shape of the piping located upstream of the throttle section.

上記目的を達成するために、本発明では、絞り部の長さを長く確保し、その絞り部の開口と対向するように冷媒衝突面を設けるようにした。 In order to achieve the above object, in the present invention, the length of the constriction part is ensured long, and the refrigerant collision surface is provided so as to face the opening of the constriction part.

第１の発明は、冷媒供給管から流入した冷媒を第１及び第２冷媒流出管に分流する冷媒分流器において、前記冷媒供給管が接続される供給路と、前記供給路の下流端部から直線状に延び、前記供給路よりも小径とされた絞り部と、前記絞り部の下流端部に連通し、前記絞り部から流入した冷媒を攪拌する略円筒形の壁面を有する冷媒攪拌室と、前記絞り部の下流端部と所定の間隔をあけて対向するように配置され、前記絞り部から流出した冷媒が衝突する冷媒衝突面と、上流端が前記冷媒攪拌室の壁面における前記冷媒衝突面から離れた部分に連通する一方、下流端が前記第１冷媒流出管に連通する第１分流路と、上流端が前記冷媒攪拌室の壁面における前記冷媒衝突面から離れた部分であってかつ前記第１分流路の上流端から離れた部分に連通する一方、下流端が前記第２冷媒流出管に連通する第２分流路とを備え、前記冷媒攪拌室は、前記絞り部の軸線と同軸上に配置されて軸線方向の長さが径方向の寸法以上とされ、前記第１分流路及び前記第２分流路は、前記絞り部の軸線に対して直交する方向に延びていることを特徴とする。 A first invention provides a refrigerant flow divider that divides refrigerant flowing from a refrigerant supply pipe into first and second refrigerant outflow pipes, and includes a supply path to which the refrigerant supply pipe is connected, and a downstream end of the supply path. a refrigerant stirring chamber that extends linearly and has a diameter smaller than that of the supply path; and a refrigerant stirring chamber that communicates with a downstream end of the constriction part and that has a substantially cylindrical wall surface that stirs the refrigerant flowing from the constriction part. , a refrigerant collision surface that is arranged to face the downstream end of the constriction part with a predetermined interval therebetween, and with which the refrigerant flowing out from the constriction part collides; a first branch channel that communicates with a portion of the wall surface of the refrigerant stirring chamber and whose downstream end communicates with the first refrigerant outflow pipe; a second branch channel that communicates with a portion remote from the upstream end of the first branch channel and whose downstream end communicates with the second refrigerant outflow pipe, and the refrigerant stirring chamber is coaxial with the axis of the constriction section. The first branch channel and the second branch channel extend in a direction perpendicular to the axis of the constriction section, and the first branch channel and the second branch channel extend in a direction perpendicular to the axis of the throttle section. shall be.

この構成によれば、冷媒供給管を流れる冷媒は、供給路に流入した後、絞り部に流入する。この絞り部が直線状に延びているので、冷媒は絞り部を流れることで流速が高められるだけでなく、絞り部から流出するときの流出方向がコントロールされる。特に、流速の高い状態の冷媒の流出方向をコントロールすることで、流出方向のコントロール性が良好になる。そして、絞り部から冷媒攪拌室に流入した冷媒は、勢いよく冷媒衝突面に衝突するので、液相冷媒と気相冷媒とが冷媒攪拌室で良好に攪拌される。冷媒攪拌室の冷媒は、攪拌された後、第１分流路及び第２分流路を介してそれぞれ第１冷媒流出管及び第２冷媒流出管に分流する。 According to this configuration, the refrigerant flowing through the refrigerant supply pipe flows into the supply path and then into the throttle section. Since the constriction extends linearly, the refrigerant not only flows through the constriction at a high flow rate, but also controls the flow direction when it flows out from the constriction. In particular, by controlling the outflow direction of the refrigerant at a high flow rate, the controllability of the outflow direction becomes better. The refrigerant flowing into the refrigerant stirring chamber from the constriction portion collides with the refrigerant collision surface with force, so that the liquid phase refrigerant and the gas phase refrigerant are well stirred in the refrigerant stirring chamber. After being stirred, the refrigerant in the refrigerant stirring chamber is divided into a first refrigerant outflow pipe and a second refrigerant outflow pipe via the first branching channel and the second branching channel, respectively.

第２の発明は、前記冷媒衝突面は、前記絞り部の下流端部から当該絞り部の軸線の延長線上に配置され、前記第１分流路及び前記第２分流路の上流端は、前記冷媒攪拌室の壁面において前記絞り部の下流端部と前記冷媒衝突面との間に開口していることを特徴とする。 In a second aspect of the present invention, the refrigerant collision surface is arranged on an extension of the axis of the throttle section from the downstream end of the throttle section, and the upstream ends of the first branch channel and the second branch channel are arranged so that the refrigerant collides with the The stirring chamber is characterized in that an opening is formed between the downstream end of the constriction portion and the refrigerant collision surface on the wall surface of the stirring chamber.

第３の発明は、前記第１分流路及び前記第２分流路の上流端は、前記絞り部の下流端部と前記冷媒衝突面との間の中央部よりも前記絞り部に近い側に開口していることを特徴とする。 A third aspect of the present invention is that the upstream ends of the first branch channel and the second branch channel are opened closer to the throttle section than a central portion between the downstream end of the throttle section and the refrigerant collision surface. It is characterized by the fact that

この構成によれば、第１分流路及び第２分流路の上流端が冷媒衝突面から離れることになるので、冷媒衝突面に衝突して十分に攪拌された状態の冷媒を第１分流路及び第２分流路の上流端に流入させることができる。 According to this configuration, the upstream ends of the first branch channel and the second branch channel are separated from the refrigerant collision surface, so that the refrigerant that has collided with the refrigerant collision surface and is sufficiently stirred is transferred to the first branch channel and the second branch channel. It can be made to flow into the upstream end of the second branch channel.

第４の発明は、前記第１分流路及び前記第２分流路の上流端は、前記冷媒攪拌室の壁面において前記延長線まわりに互いに間隔をあけて配置されていることを特徴とする。 A fourth aspect of the present invention is characterized in that the upstream ends of the first branch channel and the second branch channel are arranged at intervals around the extension line on the wall surface of the refrigerant stirring chamber.

この構成によれば、第１分流路の上流端と、第２分流路の上流端とを互いに離して配置することができるので、各々に対して十分に攪拌された状態の冷媒を流入させることができる。 According to this configuration, the upstream end of the first branch channel and the upstream end of the second branch channel can be arranged apart from each other, so that sufficiently stirred refrigerant can flow into each of them. I can do it.

第５の発明は、前記供給路及び前記絞り部が設けられた第１分流器構成部材と、前記冷媒攪拌室、前記冷媒衝突面、前記第１分流路及び前記第２分流路が設けられた第２分流器構成部材とを備え、前記第１分流器構成部材は、内部に前記絞り部が設けられ、先端面に前記絞り部の下流端が開口する突出筒部を有し、前記第２分流器構成部材は、前記突出筒部が嵌合する嵌合孔を有し、前記冷媒攪拌室は、前記嵌合孔の奥側に連通するように設けられていることを特徴とする。 A fifth invention is a first flow divider component provided with the supply channel and the throttle part, the refrigerant stirring chamber, the refrigerant collision surface, the first branch channel, and the second branch channel. a second flow divider component, wherein the first flow divider component has the constriction section provided therein, and has a protruding cylindrical section on a distal end surface of which the downstream end of the constriction section opens; The flow divider component has a fitting hole into which the protruding cylindrical portion fits, and the refrigerant stirring chamber is provided so as to communicate with a back side of the fitting hole.

この構成によれば、第１分流器構成部材と第２分流器構成部材とを一体化する際には、第１分流器構成部材の突出筒部を第２分流器構成部材の嵌合孔に嵌合させることにより、互いの相対的な位置決めを行った状態で一体化することができる。そして、第１分流器構成部材の突出筒部に絞り部を設け、第２分流器構成部材に嵌合孔に連通するように冷媒攪拌室が設けられているので、絞り部から流出した冷媒を冷媒攪拌室に流入させて攪拌することができる。 According to this configuration, when the first flow divider component and the second flow divider component are integrated, the protruding cylindrical portion of the first flow divider component is inserted into the fitting hole of the second flow divider component. By fitting them together, they can be integrated in a state where they are positioned relative to each other. Since a constriction part is provided in the protruding cylinder part of the first flow divider component, and a refrigerant stirring chamber is provided in the second flow divider component so as to communicate with the fitting hole, the refrigerant flowing out from the constriction part can be removed. The refrigerant can be stirred by flowing into the refrigerant stirring chamber.

第６の発明は、前記嵌合孔の径は、前記冷媒攪拌室の径よりも大きく設定されていることを特徴とする。 A sixth invention is characterized in that the diameter of the fitting hole is set larger than the diameter of the refrigerant stirring chamber.

この構成によれば、第２分流器構成部材の嵌合孔の径を大きくすることで、第１分流器構成部材の突出筒部が大径であっても嵌合させることができる。これにより、第１分流器構成部材の強度及び嵌合時における冷媒分流器の強度を高めることができる。また、第２分流器構成部材の嵌合孔の径が大きく、冷媒攪拌室の径が小さくなるので、嵌合孔及び冷媒攪拌室の加工が容易になる。 According to this configuration, by increasing the diameter of the fitting hole of the second flow divider component, it is possible to fit the protruding cylindrical portion of the first flow divider component even if it has a large diameter. Thereby, the strength of the first flow divider component and the strength of the refrigerant flow divider when fitted can be increased. Further, since the diameter of the fitting hole of the second flow divider component is large and the diameter of the refrigerant stirring chamber is small, machining of the fitting hole and the refrigerant stirring chamber is facilitated.

第７の発明は、前記供給路は、前記絞り部の軸線の延長線と交差する方向に延びていることを特徴とする。 A seventh aspect of the present invention is characterized in that the supply path extends in a direction intersecting an extension of the axis of the throttle section.

すなわち、供給路の延びる方向が、冷媒供給管の取り回し等の影響によって絞り部の軸線の延長線と交差する方向となる場合が考えられるが、この発明では、絞り部が直線状に延びているので、供給路の延びる方向がどのような方向であっても、絞り部によって流出方向をコントロールして冷媒衝突面に狙い通りに衝突させることができる。 In other words, it is conceivable that the direction in which the supply path extends may be in a direction that intersects the extension of the axis of the throttle part due to the influence of the routing of the refrigerant supply pipe, etc., but in this invention, the throttle part extends in a straight line. Therefore, regardless of the direction in which the supply path extends, the outflow direction can be controlled by the throttle portion to cause the refrigerant to collide with the refrigerant collision surface as intended.

第８の発明は、前記供給路は、前記絞り部の軸線の延長線と略同軸上に延びていることを特徴とする。 An eighth invention is characterized in that the supply path extends substantially coaxially with an extension of the axis of the throttle section.

この構成によれば、供給路から絞り部に至る冷媒の流れがスムーズになる。 According to this configuration, the refrigerant flows smoothly from the supply path to the throttle section.

第９の発明は、前記冷媒衝突面は、円形状とされ、前記絞り部の下流端部は、当該絞り部の軸線の延長線が前記冷媒衝突面の中心を通るように配置されていることを特徴とする。 In a ninth invention, the refrigerant collision surface has a circular shape, and the downstream end of the throttle section is arranged such that an extension of the axis of the throttle section passes through the center of the refrigerant collision surface. It is characterized by

この構成によれば、絞り部から流出した冷媒が冷媒衝突面の中心に衝突するようになるので、流れが偏り難くなり、液相冷媒と気相冷媒とを良好に攪拌することができる。 According to this configuration, the refrigerant flowing out from the throttle part collides with the center of the refrigerant collision surface, so that the flow is less likely to be biased, and the liquid phase refrigerant and the gas phase refrigerant can be stirred well.

第１０の発明は、前記冷媒衝突面と前記絞り部の軸線の延長線とが略直交していることを特徴とする。 A tenth aspect of the invention is characterized in that the refrigerant collision surface and an extension of the axis of the throttle section are substantially perpendicular to each other.

この構成によれば、冷媒の流れが冷媒衝突面に対して略直交するので、冷媒衝突面に衝突した冷媒の流れの分流性を向上させることができる。 According to this configuration, since the flow of the refrigerant is substantially perpendicular to the refrigerant collision surface, it is possible to improve the separation property of the flow of the refrigerant that collided with the refrigerant collision surface.

本発明によれば、冷媒供給管が接続される供給路の下流端部から直線状に延びる絞り部から流出した冷媒を冷媒攪拌室の冷媒衝突面に衝突させて液相冷媒と気相冷媒とを良好に混合させることができる。そして、この冷媒攪拌室に第１分流路及び第２分流路を連通させたので、絞り部の上流に位置する配管の形状に依らず、狙い通りの冷媒分流を可能にすることができる。 According to the present invention, the refrigerant flowing out from the constriction portion extending linearly from the downstream end of the supply path to which the refrigerant supply pipe is connected is made to collide with the refrigerant collision surface of the refrigerant stirring chamber to separate the liquid phase refrigerant and the gas phase refrigerant. can be mixed well. Since the first branch channel and the second branch channel are communicated with this refrigerant stirring chamber, it is possible to achieve targeted branch flow of the refrigerant regardless of the shape of the piping located upstream of the throttle section.

本発明の実施形態１に係る冷媒分流器を備えたバッテリ冷却装置の回路構成図である。FIG. 1 is a circuit configuration diagram of a battery cooling device including a refrigerant flow divider according to Embodiment 1 of the present invention. 冷媒分流器の断面図である。FIG. 3 is a cross-sectional view of a refrigerant flow divider. 第１分流器構成部材を第２分流器構成部材に固定する前の状態を示す断面図である。It is a sectional view showing the state before fixing a 1st flow divider constituent member to a 2nd flow divider constituent member. 第２分流器構成部材の平面図である。It is a top view of a 2nd flow divider component. 第２分流器構成部材の側面図である。It is a side view of a 2nd flow divider component. 第２分流器構成部材の背面図である。FIG. 3 is a rear view of the second flow divider component. 図６におけるVII－VII線断面図である。7 is a sectional view taken along the line VII-VII in FIG. 6. FIG. 本発明の実施形態２に係る図２相当図である。FIG. 3 is a diagram corresponding to FIG. 2 according to Embodiment 2 of the present invention. 図８におけるIX－IX線断面図である。9 is a sectional view taken along the line IX-IX in FIG. 8. FIG.

以下、本発明の実施形態を図面に基づいて詳細に説明する。尚、以下の好ましい実施形態の説明は、本質的に例示に過ぎず、本発明、その適用物或いはその用途を制限することを意図するものではない。 Hereinafter, embodiments of the present invention will be described in detail based on the drawings. Note that the following description of preferred embodiments is essentially just an example, and is not intended to limit the present invention, its applications, or its uses.

（実施形態１）
図１は、本発明の実施形態１に係る冷媒分流器１を備えたバッテリ冷却装置１００の回路構成図である。バッテリ冷却装置１００は、例えば、電気自動車やハイブリッド自動車（プラグインタイプを含む）等に搭載されるバッテリ２００を冷却するための装置である。バッテリ２００は、図示しないが自動車の走行用モータに電力を供給するためのものである。ハイブリッド自動車の場合、走行用モータの回生制御やエンジンによる発電機の駆動によってバッテリ２００を充電することができる。電気自動車及びプラグインタイプのハイブリッド自動車の場合、図示しない商用電源等からバッテリ２００を充電したり、走行用モータの回生制御によってバッテリ２００を充電することができる。バッテリ２００は充電時や放電時に温度上昇する。この温度上昇を抑制するためにバッテリ冷却装置１００によってバッテリ２００を冷却することができるようになっている。 (Embodiment 1)
FIG. 1 is a circuit configuration diagram of a battery cooling device 100 including a refrigerant flow divider 1 according to Embodiment 1 of the present invention. The battery cooling device 100 is, for example, a device for cooling a battery 200 mounted in an electric vehicle, a hybrid vehicle (including a plug-in type), or the like. Although not shown, the battery 200 is for supplying electric power to the motor for driving the automobile. In the case of a hybrid vehicle, the battery 200 can be charged by regenerative control of the driving motor or by driving a generator by the engine. In the case of an electric vehicle and a plug-in type hybrid vehicle, the battery 200 can be charged from a commercial power source (not shown) or by regenerative control of the driving motor. The temperature of the battery 200 increases during charging and discharging. In order to suppress this temperature rise, the battery 200 can be cooled by the battery cooling device 100.

（バッテリ冷却装置１００の構成）
バッテリ冷却装置１００は、圧縮機１０１と、コンデンサ１０２と、レシーバタンク１０３と、バッテリクーラ用膨張弁１０４と、バッテリクーラ１０５と、アキュムレータ１０６とを少なくとも備えている。この実施形態では、バッテリ冷却装置１００が車室内の空調も行えるように構成されており、従って、バッテリ冷却装置１００は、空調用空気を冷却する冷却用熱交換器としての蒸発器１０７と、空調用膨張弁１０８とを備えている。 (Configuration of battery cooling device 100)
The battery cooling device 100 includes at least a compressor 101, a condenser 102, a receiver tank 103, a battery cooler expansion valve 104, a battery cooler 105, and an accumulator 106. In this embodiment, the battery cooling device 100 is configured to also perform air conditioning in the vehicle interior, and therefore the battery cooling device 100 includes an evaporator 107 as a cooling heat exchanger that cools air conditioning air, and expansion valve 108.

圧縮機１０１は、電動コンプレッサで構成されている。圧縮機１０１から吐出された高温高圧冷媒はコンデンサ１０２に流入する。コンデンサ１０２には、ファン１０２ａによって外部空気が送風されるようになっている。コンデンサ１０２を通過した冷媒はレシーバタンク１０３に流入した後、バイパス配管１００ａと、バッテリクーラ側配管１００ｂとの一方または両方に流れるようになっている。 Compressor 101 is composed of an electric compressor. The high-temperature, high-pressure refrigerant discharged from the compressor 101 flows into the condenser 102 . External air is blown into the capacitor 102 by a fan 102a. The refrigerant that has passed through the condenser 102 flows into the receiver tank 103, and then flows into one or both of the bypass pipe 100a and the battery cooler side pipe 100b.

バッテリクーラ側配管１００ｂには、バッテリクーラ側仕切弁１００ｃが設けられている。このバッテリクーラ側仕切弁１００ｃは、バッテリクーラ側配管１００ｂを開閉するための弁である。バッテリクーラ側配管１００ｂにおけるバッテリクーラ側仕切弁１００ｃよりも下流側には、バッテリクーラ用膨張弁１０４が設けられている。バッテリクーラ用膨張弁１０４を通過した冷媒は減圧される。バッテリクーラ側配管１００ｂにおけるバッテリクーラ用膨張弁１０４よりも下流側には、本発明に係る分媒分流器１が設けられている。 A battery cooler side gate valve 100c is provided in the battery cooler side piping 100b. This battery cooler side gate valve 100c is a valve for opening and closing the battery cooler side piping 100b. A battery cooler expansion valve 104 is provided downstream of the battery cooler side gate valve 100c in the battery cooler side piping 100b. The refrigerant that has passed through the battery cooler expansion valve 104 is depressurized. A dispersion flow divider 1 according to the present invention is provided downstream of the battery cooler expansion valve 104 in the battery cooler side piping 100b.

分媒分流器１は、バッテリクーラ側配管（冷媒供給管）１００ｂから流入した冷媒を第１冷媒流出管１００ｆ及び第２冷媒流出管１００ｇに分流するためのものである。すなわち、バッテリクーラ１０５は、バッテリ２００を冷却するための冷熱を当該バッテリ２００に供給する熱交換器（蒸発器）で構成されているが、このバッテリクーラ１０５には、図示しないが複数のチューブが設けられている。各チューブに冷媒を分流させるために分媒分流器１が設けられている。本例では、冷媒を２つに分流する場合について説明するが、冷媒は３つ以上に分流することもできる。また、分媒分流器１は、第１冷媒流出管１００ｆ及び第２冷媒流出管１００ｇに冷媒を均等に分流させてもよいし、一方への分流量が他方への分流量に比べて多くなるように分流させてもよい。 The separator flow divider 1 is for dividing the refrigerant flowing from the battery cooler side pipe (refrigerant supply pipe) 100b into the first refrigerant outflow pipe 100f and the second refrigerant outflow pipe 100g. That is, the battery cooler 105 is composed of a heat exchanger (evaporator) that supplies cold heat to the battery 200 to cool the battery 200, but the battery cooler 105 includes a plurality of tubes (not shown). It is provided. A separator flow divider 1 is provided to divide the refrigerant into each tube. In this example, a case will be described in which the refrigerant is divided into two streams, but the refrigerant can also be divided into three or more streams. Further, the separator flow divider 1 may divide the refrigerant equally between the first refrigerant outflow pipe 100f and the second refrigerant outflow pipe 100g, or the amount of the refrigerant diverted to one side may be larger than the amount of diversion to the other side. The flow may be divided as follows.

バッテリクーラ側配管１００ｂ、第１冷媒流出管１００ｆ及び第２冷媒流出管１００ｇは全て同径であってもよいし、径が異なっていてもよい。また、バッテリクーラ側配管１００ｂ、第１冷媒流出管１００ｆ及び第２冷媒流出管１００ｇは、例えばアルミニウム合金製の配管部材で構成されている。さらに、バッテリクーラ側配管１００ｂ、第１冷媒流出管１００ｆ及び第２冷媒流出管１００ｇの断面は略円形とされている。 The battery cooler side pipe 100b, the first refrigerant outflow pipe 100f, and the second refrigerant outflow pipe 100g may all have the same diameter or may have different diameters. Further, the battery cooler side piping 100b, the first refrigerant outflow pipe 100f, and the second refrigerant outflow pipe 100g are made of, for example, aluminum alloy piping members. Furthermore, the cross sections of the battery cooler side pipe 100b, the first refrigerant outflow pipe 100f, and the second refrigerant outflow pipe 100g are approximately circular.

バイパス配管１００ａには、バイパス側仕切弁１００ｄが設けられている。このバイパス側仕切弁１００ｄは、バイパス配管１００ａを開閉するための弁である。バイパス配管１００ａは蒸発器１０７に接続されている。バイパス配管１００ａにおけるバイパス側仕切弁１００ｄよりも下流側には、空調用膨張弁１０８が設けられている。蒸発器１０７から流出した冷媒は、アキューレータ１０６に流入した後、圧縮機１０１に吸入される。尚、蒸発器１０７には、ブロワ１２０によって空調用空気が送風されるようになっている。空調用空気が蒸発器１０７により冷却された後、車室に供給される。 A bypass side gate valve 100d is provided in the bypass pipe 100a. This bypass side gate valve 100d is a valve for opening and closing the bypass piping 100a. Bypass piping 100a is connected to evaporator 107. An air conditioning expansion valve 108 is provided downstream of the bypass side gate valve 100d in the bypass piping 100a. The refrigerant flowing out of the evaporator 107 flows into the accurator 106 and then is sucked into the compressor 101. Note that air conditioning air is blown to the evaporator 107 by a blower 120. After the air-conditioning air is cooled by the evaporator 107, it is supplied to the vehicle interior.

したがって、バッテリクーラ側仕切弁１００ｃ及びバイパス側仕切弁１００ｄの開閉動作により、冷媒をバッテリクーラ１０５のみに流すモードと、冷媒を蒸発器１０７にのみ流す動作と、冷媒をバッテリクーラ１０５と蒸発器１０７の両方に流すモードとのうち、任意のモードに切り替えることができる。 Therefore, by opening and closing the battery cooler side gate valve 100c and the bypass side gate valve 100d, there are modes in which the refrigerant flows only to the battery cooler 105, an operation in which the refrigerant flows only to the evaporator 107, and a mode in which the refrigerant flows only to the battery cooler 105 and the evaporator 107. You can switch to any mode between the two modes.

（冷媒分流器１の構成）
図２及び図３に示すように、冷媒分流器１は、第１分流器構成部材１０と、第２分流器構成部材２０とを備えている。第１分流器構成部材１０及び第２分流器構成部材２０は、例えばアルミニウム合金製のブロック材等で構成されている。第１分流器構成部材１０は、基部１１と、基部１１から突出する突出筒部１２とを備えている。突出筒部１２の断面形状は円形である。基部１１及び突出筒部１２は一体成形されていてもよいし、基部１１及び突出筒部１２を別部材で形成した後、組み合わせて一体化してもよい。 (Configuration of refrigerant flow divider 1)
As shown in FIGS. 2 and 3, the refrigerant flow divider 1 includes a first flow divider component 10 and a second flow divider component 20. The first flow divider component 10 and the second flow divider component 20 are made of, for example, an aluminum alloy block material. The first flow divider component 10 includes a base 11 and a protruding cylindrical portion 12 that protrudes from the base 11. The cross-sectional shape of the protruding cylindrical portion 12 is circular. The base 11 and the protruding cylindrical part 12 may be integrally molded, or the base 11 and the protruding cylindrical part 12 may be formed from separate members and then combined to be integrated.

基部１１には、バッテリクーラ側配管１００ｂの下流端部が差し込まれた状態で接続される供給側配管接続孔１１ａが形成されている。供給側配管接続孔１１ａの断面形状は円形である。バッテリクーラ側配管１００ｂの外周面は、供給側配管接続孔１１ａの内周面に対して全周にわたってろう付けされている。 A supply side piping connection hole 11a is formed in the base 11, into which the downstream end of the battery cooler side piping 100b is inserted and connected. The cross-sectional shape of the supply side piping connection hole 11a is circular. The outer peripheral surface of the battery cooler side piping 100b is brazed to the inner peripheral surface of the supply side piping connection hole 11a over the entire circumference.

基部１１には、供給側配管接続孔１１ａの奥側（冷媒流れ方向下流側）に連通する供給路１１ｂが設けられている。供給側配管接続孔１１ａは基部１１の上面に開口している。供給路１１ｂの断面形状は供給側配管接続孔１１ａの断面形状よりも小さい円形とされている。供給路１１ｂはまっすぐに延びており、供給路１１ｂの軸線と、供給側配管接続孔１１ａの軸線とは一致している。供給路１１ｂと供給側配管接続孔１１ａとの境界部分には段部１１ｃが形成されている。バッテリクーラ側配管１００ｂの下流端部は供給側配管接続孔１１ａに差し込まれた状態で段部１１ｃに当接することによって差し込み深さが設定されている。バッテリクーラ側配管１００ｂは、供給側配管接続孔１１ａに差し込まれた状態で供給路１１ｂと接続される。 The base portion 11 is provided with a supply path 11b that communicates with the back side (downstream side in the refrigerant flow direction) of the supply side piping connection hole 11a. The supply side piping connection hole 11a is open on the upper surface of the base 11. The cross-sectional shape of the supply passage 11b is circular, which is smaller than the cross-sectional shape of the supply-side piping connection hole 11a. The supply path 11b extends straight, and the axis of the supply path 11b and the axis of the supply side piping connection hole 11a coincide. A step portion 11c is formed at the boundary between the supply path 11b and the supply side piping connection hole 11a. The downstream end of the battery cooler side piping 100b is inserted into the supply side piping connection hole 11a and comes into contact with the stepped portion 11c, thereby setting the insertion depth. The battery cooler side piping 100b is inserted into the supply side piping connection hole 11a and connected to the supply path 11b.

供給路１１ｂの下流端部は、テーパ面１１ｄで構成されている。テーパ面１１ｄは、冷媒流れ方向の下流側へ向かって縮径するように形成されている。テーパ面１１ｄの軸線と、供給路１１ｂの軸線とは一致している。 The downstream end of the supply path 11b is configured with a tapered surface 11d. The tapered surface 11d is formed so as to decrease in diameter toward the downstream side in the coolant flow direction. The axis of the tapered surface 11d and the axis of the supply path 11b match.

第１分流器構成部材１０には、供給路１１ｂの下流端部から直線状に延び、供給路１１ｂにおけるテーパ面１１ｄ以外の部分よりも小径とされた絞り部１２ａが設けられている。具体的には、第１分流器構成部材１０の突出筒部１２の内部に絞り部１２ａが設けられている。絞り部１２ａの下流端は、突出筒部１２の先端面においてその中心部に開口している。絞り部１２ａの断面形状は円形であり、突出筒部１２の先端面に開口する絞り部１２ａの下流端も同様に円形である。絞り部１２ａの径は、その上流端から下流端まで等しく設定されている。絞り部１２ａの長さは、供給路１１ｂのテーパ面１１ｄを含んだ長さよりも長く設定されている。これにより、絞り部１２ａは、同一内径が所定長さにわたって連続する形状になる。 The first flow divider component 10 is provided with a constricted portion 12a that extends linearly from the downstream end of the supply path 11b and has a diameter smaller than that of the portion of the supply path 11b other than the tapered surface 11d. Specifically, a constricted portion 12a is provided inside the protruding cylindrical portion 12 of the first flow divider component 10. The downstream end of the constricted portion 12a opens at the center of the distal end surface of the protruding cylindrical portion 12. The cross-sectional shape of the constricted portion 12a is circular, and the downstream end of the constricted portion 12a that opens at the distal end surface of the protruding cylindrical portion 12 is also circular. The diameter of the constricted portion 12a is set to be equal from its upstream end to its downstream end. The length of the constricted portion 12a is set longer than the length including the tapered surface 11d of the supply path 11b. As a result, the constricted portion 12a has a shape in which the same inner diameter continues over a predetermined length.

絞り部１２ａの長さ寸法と、絞り部１２ａの径とを比較すると、長さ寸法の方が長くなっている。絞り部１２ａの長さは、例えば７ｍｍ以上に設定することができ、好ましくは１０ｍｍ以上である。また、絞り部１２ａの内径は、例えば単位面積当たりの冷媒流量が１．０～４．０ｇ／ｓ・ｍｍ２の範囲内となるように設定することができる。この範囲に設定することで、後述する冷媒攪拌室での液相冷媒と気相冷媒との混合が良好になるとともに、圧力損失を低減することができる。尚、絞り部１２ａの一部は基部１１の内部に形成されていてもよい。 Comparing the length of the constricted portion 12a and the diameter of the constricted portion 12a, the length is longer. The length of the constricted portion 12a can be set to, for example, 7 mm or more, and preferably 10 mm or more. Further, the inner diameter of the constricted portion 12a can be set so that the flow rate of refrigerant per unit area is within a range of 1.0 to 4.0 g/s·mm 2 , for example. By setting within this range, the liquid phase refrigerant and the gas phase refrigerant can be mixed well in the refrigerant stirring chamber described later, and pressure loss can be reduced. Note that a part of the constricted portion 12a may be formed inside the base portion 11.

突出筒部１２の外周面には、環状溝１２ｂが形成されている。環状溝１２ｂには、ゴム等からなるシール材としてのＯリング１３が嵌め込まれている。 An annular groove 12b is formed on the outer circumferential surface of the protruding cylindrical portion 12. An O-ring 13 as a sealing material made of rubber or the like is fitted into the annular groove 12b.

第２分流器構成部材２０は、突出筒部１２が嵌合する嵌合孔２１を有している。嵌合孔２１は、第２分流器構成部材２０の上面に開口しており、その断面形状は円形である。嵌合孔２１の長さは、突出筒部１２の突出長さと略等しく設定されている。従って、突出筒部１２を嵌合孔２１に差し込んで嵌合させると、第１分流器構成部材１０の基部１１の下面が、第２分流器構成部材２０の上面に当接する。この状態で図示しないがボルト等によって第１分流器構成部材１０と第２分流器構成部材２０とを締結することができるようになっている。図４には、そのボルトが螺合するねじ孔２０ａを示している。突出筒部１２を嵌合孔２１に差し込むと、Ｏリング１３によって両者の間がシールされる。 The second flow divider component 20 has a fitting hole 21 into which the protruding cylindrical portion 12 fits. The fitting hole 21 opens on the upper surface of the second flow divider component 20, and has a circular cross-sectional shape. The length of the fitting hole 21 is set to be approximately equal to the protruding length of the protruding cylindrical portion 12 . Therefore, when the protruding cylindrical portion 12 is inserted into the fitting hole 21 and fitted, the lower surface of the base 11 of the first flow divider component 10 comes into contact with the upper surface of the second flow divider component 20. In this state, the first flow divider component 10 and the second flow divider component 20 can be fastened together with bolts or the like (not shown). FIG. 4 shows a screw hole 20a into which the bolt is screwed. When the protruding cylindrical portion 12 is inserted into the fitting hole 21, the space between the two is sealed by the O-ring 13.

第２分流器構成部材２０には、嵌合孔２１の奥側に、冷媒攪拌室２２が設けられている。冷媒攪拌室２２は、嵌合孔２１の奥側に連通している。冷媒攪拌室２２の断面形状は嵌合孔２１の断面形状よりも小さな円形である。従って、嵌合孔２１の径は、冷媒攪拌室２２の径よりも大きく設定されており、嵌合孔２１と冷媒攪拌室２２との境界部分に段部２０ｂが形成されることになる。段部２０ｂはテーパ面で構成することができる。また、図４に示すように、冷媒攪拌室２２の断面形状が嵌合孔２１の断面形状よりも小さいので、冷媒攪拌室２２及び嵌合孔２１を形成するときに、例えば回転工具を用いて冷媒攪拌室２２を先に形成し、嵌合孔２１を後に形成することや、嵌合孔２１を先に形成し、冷媒攪拌室２２を後に形成することができる。 The second flow divider component 20 is provided with a refrigerant stirring chamber 22 on the back side of the fitting hole 21 . The refrigerant stirring chamber 22 communicates with the inner side of the fitting hole 21 . The cross-sectional shape of the refrigerant stirring chamber 22 is a circle smaller than the cross-sectional shape of the fitting hole 21. Therefore, the diameter of the fitting hole 21 is set larger than the diameter of the refrigerant stirring chamber 22, and a stepped portion 20b is formed at the boundary between the fitting hole 21 and the refrigerant stirring chamber 22. The step portion 20b can be configured with a tapered surface. Furthermore, as shown in FIG. 4, since the cross-sectional shape of the refrigerant stirring chamber 22 is smaller than the cross-sectional shape of the fitting hole 21, when forming the refrigerant stirring chamber 22 and the fitting hole 21, for example, a rotary tool is used to form the refrigerant stirring chamber 22 and the fitting hole 21. The refrigerant stirring chamber 22 can be formed first and the fitting hole 21 can be formed later, or the fitting hole 21 can be formed first and the refrigerant stirring chamber 22 can be formed later.

第１分流器構成部材１０を第２分流器構成部材２０に固定することで、絞り部１２ａの下流端部と、冷媒攪拌室２２とが連通する。冷媒攪拌室２２は、絞り部１２ａから流入した冷媒を攪拌するための空間を形成している。冷媒攪拌室２２の軸線方向の長さは、絞り部１２ａの長さと同程度に設定することができるが、絞り部１２ａの長さより長くてもよいし、短くてもよい。具体的には、図２に示すように、冷媒攪拌室２２の軸線方向の長さＢは、１０ｍｍ以上、好ましくは１５ｍｍ以上に設定することができる。 By fixing the first flow divider component 10 to the second flow divider component 20, the downstream end of the throttle section 12a and the refrigerant stirring chamber 22 communicate with each other. The refrigerant stirring chamber 22 forms a space for stirring the refrigerant flowing in from the constricted portion 12a. The length of the refrigerant stirring chamber 22 in the axial direction can be set to be approximately the same as the length of the throttle part 12a, but may be longer or shorter than the length of the throttle part 12a. Specifically, as shown in FIG. 2, the axial length B of the refrigerant stirring chamber 22 can be set to 10 mm or more, preferably 15 mm or more.

冷媒攪拌室２２の径は、絞り部１２ａの径よりも十分に大きく設定されており、絞り部１２ａから流入した冷媒を攪拌させるのに必要十分な空間を冷媒攪拌室２２内に確保できるようになっている。絞り部１２ａから流入した冷媒は、バッテリクーラ用膨張弁１０４を流通しているので、液相冷媒と気相冷媒とが混合した気液二層冷媒となっていることがある。この気液二層冷媒を冷媒攪拌室２２で攪拌することで、液相冷媒と気相冷媒とを混合することができる。 The diameter of the refrigerant stirring chamber 22 is set to be sufficiently larger than the diameter of the constricted part 12a, so that a sufficient space can be secured in the refrigerant stirring chamber 22 to stir the refrigerant flowing in from the constricted part 12a. It has become. Since the refrigerant that has flowed in from the throttle portion 12a flows through the battery cooler expansion valve 104, it may become a gas-liquid two-layer refrigerant in which a liquid phase refrigerant and a gas phase refrigerant are mixed. By stirring this gas-liquid two-layer refrigerant in the refrigerant stirring chamber 22, the liquid phase refrigerant and the gas phase refrigerant can be mixed.

第２分流器構成部材２０には、絞り部１２ａから流出した冷媒が衝突する冷媒衝突面２４が設けられている。冷媒衝突面２４は、絞り部１２ａの下流端部と所定の間隔をあけて対向するように配置されている。冷媒衝突面２４は、円形状とされている。冷媒衝突面２４は、絞り部１２ａの下流端部から当該絞り部１２ａの軸線の延長線上に配置されている。絞り部１２ａの下流端部は、当該絞り部１２ａの軸線の延長線が冷媒衝突面２４の中心を通るように配置されている。冷媒衝突面２４は、平坦面で構成されていてもよいし、湾曲面で構成されていてもよい。冷媒衝突面２４が平坦面である場合、冷媒衝突面２４と絞り部１２ａの軸線の延長線とが略直交している。 The second flow divider component 20 is provided with a refrigerant collision surface 24 against which the refrigerant flowing out from the throttle portion 12a collides. The refrigerant collision surface 24 is arranged to face the downstream end of the constriction portion 12a with a predetermined distance therebetween. The refrigerant collision surface 24 has a circular shape. The refrigerant collision surface 24 is arranged on an extension of the axis of the throttle section 12a from the downstream end of the throttle section 12a. The downstream end of the throttle part 12a is arranged so that an extension of the axis of the throttle part 12a passes through the center of the refrigerant collision surface 24. The refrigerant collision surface 24 may be configured as a flat surface or may be configured as a curved surface. When the refrigerant collision surface 24 is a flat surface, the refrigerant collision surface 24 and the extension line of the axis of the throttle portion 12a are substantially perpendicular to each other.

第２分流器構成部材２０には、第１分流路２５と、第２分流路２６とが設けられている。第１分流路２５及び第２分流路２６の上流端は、それぞれ、冷媒攪拌室２２における冷媒衝突面２４から離れた部分に連通している。すなわち、第１分流路２５及び第２分流路２６の上流端は、冷媒攪拌室２２の壁面における絞り部１２ａの下流端部と冷媒衝突面２４との間に開口している。より具体的には、第１分流路２５及び第２分流路２６の上流端は、絞り部１２ａの下流端部と冷媒衝突面２４との間の中央部よりも絞り部１２ａに近い側に開口している。これにより、冷媒衝突面２４と、第１分流路２５及び第２分流路２６の上流端とを離すことができる。図２に示すように、冷媒衝突面２４と、第１分流路２５及び第２分流路２６の上流端の中心部との離間距離Ａは、９ｍｍ以上１３．５ｍｍ以下に設定することができる。尚、第１分流路２５及び第２分流路２６の上流端は、絞り部１２ａの下流端部と冷媒衝突面２４との間の中央部に開口していてもよいし、中央部よりも冷媒衝突面２４に近い側に開口していてもよい。 The second flow divider component 20 is provided with a first flow divider 25 and a second flow divider 26 . The upstream ends of the first branch channel 25 and the second branch channel 26 each communicate with a portion of the refrigerant stirring chamber 22 that is remote from the refrigerant collision surface 24 . That is, the upstream ends of the first branch channel 25 and the second branch channel 26 open between the downstream end of the throttle section 12 a on the wall surface of the refrigerant stirring chamber 22 and the refrigerant collision surface 24 . More specifically, the upstream ends of the first branch channel 25 and the second branch channel 26 are opened closer to the throttle section 12a than the center between the downstream end of the throttle section 12a and the refrigerant collision surface 24. are doing. Thereby, the refrigerant collision surface 24 and the upstream ends of the first branch channel 25 and the second branch channel 26 can be separated. As shown in FIG. 2, the separation distance A between the refrigerant collision surface 24 and the center portions of the upstream ends of the first branch channel 25 and the second branch channel 26 can be set to 9 mm or more and 13.5 mm or less. Note that the upstream ends of the first branch channel 25 and the second branch channel 26 may be opened at the center between the downstream end of the constriction part 12a and the refrigerant collision surface 24, or the It may be open on the side closer to the collision surface 24.

第１分流路２５及び第２分流路２６の上流端は、冷媒攪拌室２２の壁面において絞り部１２ａの軸線の延長線まわりに互いに間隔をあけて配置されている。つまり、第１分流路２５の上流端と、第２分流路２６の上流端とは、冷媒攪拌室２２の壁面の周方向に互いに間隔あけて配置されており、周方向に所定距離だけ離間している。図７に示すように、第１分流路２５及び第２分流路２６は、その上流端同士が最も接近しており、下流端に近づくにつれて互いの離間距離が長くなっている。 The upstream ends of the first branch channel 25 and the second branch channel 26 are arranged at intervals on the wall surface of the refrigerant stirring chamber 22 around an extension of the axis of the throttle section 12a. That is, the upstream end of the first branch channel 25 and the upstream end of the second branch channel 26 are arranged at intervals from each other in the circumferential direction of the wall surface of the refrigerant stirring chamber 22, and are spaced apart by a predetermined distance in the circumferential direction. ing. As shown in FIG. 7, the first branch channel 25 and the second branch channel 26 are closest to each other at their upstream ends, and the distance between them becomes longer as they approach their downstream ends.

第２分流器構成部材２０には、第１冷媒流出管１００ｆの上流端部が差し込まれた状態で接続される第１流出側配管接続孔２０ｃが形成されている。第１流出側配管接続孔２０ｃの断面形状は円形である。第１流出側配管接続孔２０ｃの軸線と、第１分流路２５の軸線とは互いに交差する位置関係となっている。また、第１分流路２５の下流端は、第１流出側配管接続孔２０ｃの軸線から径方向に離れた部分と連通している。第１冷媒流出管１００ｆの外周面は、第１流出側配管接続孔２０ｃの内周面に対して全周にわたってろう付けされている。これにより、第１分流路２５の下流端と、第１冷媒流出管１００ｆの上流端部とが連通する。 The second flow divider component 20 is formed with a first outflow side pipe connection hole 20c into which the upstream end of the first refrigerant outflow pipe 100f is inserted and connected. The cross-sectional shape of the first outflow side piping connection hole 20c is circular. The axis of the first outflow side piping connection hole 20c and the axis of the first branch channel 25 are in a positional relationship that intersects with each other. Further, the downstream end of the first branch flow path 25 communicates with a portion radially away from the axis of the first outflow side piping connection hole 20c. The outer peripheral surface of the first refrigerant outflow pipe 100f is brazed to the inner peripheral surface of the first outflow side pipe connection hole 20c over the entire circumference. Thereby, the downstream end of the first branch flow path 25 and the upstream end of the first refrigerant outflow pipe 100f communicate with each other.

また、第２分流器構成部材２０には、第２冷媒流出管１００ｇの上流端部が差し込まれた状態で接続される第２流出側配管接続孔２０ｄが形成されている。第２流出側配管接続孔２０ｄの断面形状は円形である。第２流出側配管接続孔２０ｄの軸線と、第２分流路２６の軸線とは互いに交差する位置関係となっている。また、第２分流路２６の下流端は、第２流出側配管接続孔２０ｄの軸線から径方向に離れた部分と連通している。第２冷媒流出管１００ｇの外周面は、第２流出側配管接続孔２０ｄの内周面に対して全周にわたってろう付けされている。これにより、第２分流路２６の下流端と、第２冷媒流出管１００ｇの上流端部とが連通する。 Further, the second flow divider component 20 is formed with a second outflow side pipe connection hole 20d into which the upstream end of the second refrigerant outflow pipe 100g is inserted and connected. The cross-sectional shape of the second outflow side piping connection hole 20d is circular. The axis of the second outflow side piping connection hole 20d and the axis of the second branch flow path 26 are in a positional relationship that intersects with each other. Further, the downstream end of the second branch flow path 26 communicates with a portion radially away from the axis of the second outflow side piping connection hole 20d. The outer peripheral surface of the second refrigerant outflow pipe 100g is brazed to the inner peripheral surface of the second outflow side pipe connection hole 20d over the entire circumference. Thereby, the downstream end of the second branch flow path 26 and the upstream end of the second refrigerant outflow pipe 100g communicate with each other.

（実施形態の作用効果）
したがって、図３に示すように、気液二層冷媒がバッテリクーラ側配管１００ｂから供給路１１ｂに流入すると、気液二層冷媒を絞り部１２ａに流入させることができる。この絞り部１２ａが直線状に延びていて所定の長さを有しているので、冷媒は絞り部１２ａを流れることで流速が高められるだけでなく、絞り部１２ａから流出するときの流出方向がコントロールされる。特に、流速の高い状態の冷媒の流出方向をコントロールすることで、流出方向のコントロール性が良好になる。そして、絞り部１２ａから冷媒攪拌室２２に流入した冷媒は、勢いよく冷媒衝突面２４に衝突するので、液相冷媒と気相冷媒とが冷媒攪拌室２２で良好に攪拌される。攪拌された後、冷媒攪拌室２２の冷媒は、第１分流路２５及び第２分流路２６を介してそれぞれ第１冷媒流出管１００ｆ及び第２冷媒流出管１００ｇに均一に分流する。 (Operations and effects of embodiments)
Therefore, as shown in FIG. 3, when the gas-liquid two-layer refrigerant flows into the supply path 11b from the battery cooler side piping 100b, the gas-liquid two-layer refrigerant can be caused to flow into the throttle part 12a. Since the constricted part 12a extends linearly and has a predetermined length, the refrigerant not only increases the flow velocity by flowing through the constricted part 12a, but also the outflow direction when flowing out from the constricted part 12a. be controlled. In particular, by controlling the outflow direction of the refrigerant at a high flow rate, the controllability of the outflow direction becomes better. The refrigerant flowing into the refrigerant stirring chamber 22 from the constriction portion 12a collides with the refrigerant collision surface 24 with force, so that the liquid phase refrigerant and the gas phase refrigerant are well stirred in the refrigerant stirring chamber 22. After being stirred, the refrigerant in the refrigerant stirring chamber 22 is uniformly divided into the first refrigerant outflow pipe 100f and the second refrigerant outflow pipe 100g via the first branching channel 25 and the second branching channel 26, respectively.

また、冷媒分流器１の直上流に位置する配管が屈曲している場合には、冷媒分流器１に流入する冷媒の流速分布に偏りが発生するが、この実施形態では、絞り部１２ａが直線状であるため、絞り部１２ａの内部を流れる間に冷媒の流速分布の偏りを小さくすることができる。これにより、冷媒分流器１の直上流に位置する配管の形状に依らず、冷媒の分流を均一化することができる。 Furthermore, if the piping located immediately upstream of the refrigerant flow divider 1 is bent, the flow velocity distribution of the refrigerant flowing into the refrigerant flow divider 1 will be biased, but in this embodiment, the constricted portion 12a is straight. Since the refrigerant has a shape, it is possible to reduce the deviation in the flow velocity distribution of the refrigerant while flowing inside the constricted portion 12a. Thereby, regardless of the shape of the pipe located immediately upstream of the refrigerant flow divider 1, the refrigerant flow can be made uniform.

（実施形態２）
図８は、本発明の実施形態２に係るものである。実施形態２は、冷媒を４方向に分流する点と、バッテリクーラ側配管１００ｂ及び絞り部１２ａの軸線方向が互いに交差する位置関係になっている点とで実施形態１のものと異なっている。以下、実施形態１と同じ部分には同じ符号を付して説明を省略し、異なる部分について詳細に説明する。 (Embodiment 2)
FIG. 8 relates to Embodiment 2 of the present invention. Embodiment 2 differs from Embodiment 1 in that the refrigerant is divided into four directions and that the axial directions of the battery cooler side piping 100b and the throttle section 12a are in a positional relationship that intersects with each other. Hereinafter, the same parts as in Embodiment 1 will be given the same reference numerals and the explanation will be omitted, and different parts will be explained in detail.

実施形態２では、供給路１１ｂが絞り部１２ａの軸線の延長線と交差する方向に延びている。すなわち、図８に示すように、供給路１１ｂは、水平方向に延びるように形成される一方、絞り部１２ａは上下方向に延びるように形成されている。これにより、供給路１１ｂの延びる方向と、絞り部１２ａの軸線とが略直交する位置関係になる。 In the second embodiment, the supply path 11b extends in a direction intersecting the extension of the axis of the constricted portion 12a. That is, as shown in FIG. 8, the supply path 11b is formed to extend in the horizontal direction, while the constricted portion 12a is formed to extend in the vertical direction. This creates a positional relationship in which the direction in which the supply path 11b extends and the axis of the throttle portion 12a are substantially orthogonal.

また、図９に示すように、第２分流器構成部材２０には、第１分流路２５及び第２分流路２６の他に、第３分流路２７と第４分流路２８とが設けられている。第２分流器構成部材２０には、第３冷媒流出管（図示せず）の上流端部が差し込まれた状態で接続される第３流出側配管接続孔２０ｅが形成されている。第３分流路２７の下流端は、第３流出側配管接続孔２０ｅと連通している。また、第２分流器構成部材２０には、第４冷媒流出管（図示せず）の上流端部が差し込まれた状態で接続される第４流出側配管接続孔２０ｆが形成されている。第４分流路２８の下流端は、第４流出側配管接続孔２０ｆと連通している。 Further, as shown in FIG. 9, the second flow divider component 20 is provided with a third flow flow path 27 and a fourth flow flow separation path 28 in addition to the first flow flow path 25 and the second flow flow separation path 26. There is. The second flow divider component 20 is formed with a third outlet pipe connection hole 20e into which the upstream end of a third refrigerant outlet pipe (not shown) is inserted and connected. The downstream end of the third branch flow path 27 communicates with the third outflow side piping connection hole 20e. Further, the second flow divider component 20 is formed with a fourth outlet pipe connection hole 20f into which the upstream end of a fourth refrigerant outlet pipe (not shown) is inserted and connected. The downstream end of the fourth branch flow path 28 communicates with the fourth outflow side piping connection hole 20f.

この実施形態２によれば、実施形態１と同様な作用効果を奏することができるとともに、冷媒を４方向に分流することができる。また、供給路１１ｂの延びる方向が、配管の取り回し等の影響によって絞り部１２ａの軸線の延長線と交差する方向となった場合に、絞り部１２ａが直線状に延びているので、供給路１１ｂの延びる方向がどのような方向であっても、絞り部１２ａによって流出方向をコントロールして冷媒衝突面２４に狙い通りに衝突させることができる。 According to the second embodiment, the same effects as those of the first embodiment can be achieved, and the refrigerant can be divided into four directions. Furthermore, when the direction in which the supply path 11b extends crosses the extension of the axis of the constricted portion 12a due to the influence of piping layout, etc., since the constricted portion 12a extends linearly, the supply path 11b Regardless of the direction in which the refrigerant extends, the flow direction can be controlled by the constriction portion 12a to cause the refrigerant to collide with the refrigerant collision surface 24 as intended.

上述の実施形態はあらゆる点で単なる例示に過ぎず、限定的に解釈してはならない。さらに、特許請求の範囲の均等範囲に属する変形や変更は、全て本発明の範囲内のものである。上記冷媒分流器１は、バッテリ冷却装置１００だけでなく、空調装置の熱交換器を構成するチューブに冷媒を分流させる場合にも適用することができる。また、第１分流路２５、第２分流路２６、第３分流路２７及び第４分流路２８の延びる方向は任意の方向にすることができる。また、分流路の数は、３つであってもよいし、５つ以上であってもよい。 The embodiments described above are merely illustrative in all respects and should not be interpreted in a limiting manner. Furthermore, all modifications and changes that come within the scope of equivalents of the claims are intended to be within the scope of the present invention. The refrigerant flow divider 1 can be applied not only to the battery cooling device 100 but also to the case where refrigerant is divided into tubes forming a heat exchanger of an air conditioner. Further, the first branch channel 25, the second branch channel 26, the third branch channel 27, and the fourth branch channel 28 can extend in any direction. Moreover, the number of branch channels may be three, or may be five or more.

以上説明したように、本発明に係る冷媒分流器は、例えばバッテリ冷却装置や空調装置に利用することができる。 As explained above, the refrigerant flow divider according to the present invention can be used, for example, in a battery cooling device or an air conditioner.

１ 冷媒分流器
１０ 第１分流器構成部材
１１ｂ 供給路
１２ 突出筒部
１２ａ 絞り部
２０ 第２分流器構成部材
２１ 嵌合孔
２２ 冷媒攪拌室
２４ 冷媒衝突面
２５ 第１分流路
２６ 第２分流路
１００ｂ バッテリクーラ側配管（冷媒供給管）
１００ｆ 第１冷媒流出管
１００ｇ 第２冷媒流出管 1 Refrigerant flow divider 10 First flow divider component 11b Supply path 12 Projecting tube portion 12a Throttle portion 20 Second flow divider component 21 Fitting hole 22 Refrigerant stirring chamber 24 Refrigerant collision surface 25 First flow divider 26 Second flow divider 100b Battery cooler side piping (refrigerant supply pipe)
100f First refrigerant outflow pipe 100g Second refrigerant outflow pipe

Claims (10)

冷媒供給管から流入した冷媒を第１及び第２冷媒流出管に分流する冷媒分流器において、
前記冷媒供給管が接続される供給路と、
前記供給路の下流端部から直線状に延び、前記供給路よりも小径とされた絞り部と、
前記絞り部の下流端部に連通し、前記絞り部から流入した冷媒を攪拌する略円筒形の壁面を有する冷媒攪拌室と、
前記絞り部の下流端部と所定の間隔をあけて対向するように配置され、前記絞り部から流出した冷媒が衝突する冷媒衝突面と、
上流端が前記冷媒攪拌室の壁面における前記冷媒衝突面から離れた部分に連通する一方、下流端が前記第１冷媒流出管に連通する第１分流路と、
上流端が前記冷媒攪拌室の壁面における前記冷媒衝突面から離れた部分であってかつ前記第１分流路の上流端から離れた部分に連通する一方、下流端が前記第２冷媒流出管に連通する第２分流路とを備え、
前記冷媒攪拌室は、前記絞り部の軸線と同軸上に配置されて軸線方向の長さが径方向の寸法以上とされ、
前記第１分流路及び前記第２分流路は、前記絞り部の軸線に対して直交する方向に延びていることを特徴とする冷媒分流器。 A refrigerant flow divider that divides refrigerant flowing from a refrigerant supply pipe into first and second refrigerant outflow pipes,
a supply path to which the refrigerant supply pipe is connected;
a constriction portion extending linearly from a downstream end of the supply path and having a diameter smaller than that of the supply path;
a refrigerant stirring chamber communicating with a downstream end of the constriction part and having a substantially cylindrical wall surface for stirring the refrigerant flowing from the constriction part;
a refrigerant collision surface that is arranged to face the downstream end of the constriction part with a predetermined distance therebetween, and on which the refrigerant flowing out from the constriction part collides;
a first branch channel whose upstream end communicates with a portion of the wall surface of the refrigerant stirring chamber that is remote from the refrigerant collision surface, and whose downstream end communicates with the first refrigerant outflow pipe;
The upstream end communicates with a portion of the wall surface of the refrigerant stirring chamber that is remote from the refrigerant collision surface and is remote from the upstream end of the first branch flow path, while the downstream end communicates with the second refrigerant outflow pipe. and a second branch flow path,
The refrigerant stirring chamber is arranged coaxially with the axis of the throttle part, and the length in the axial direction is greater than or equal to the dimension in the radial direction,
The refrigerant flow divider, wherein the first branch flow path and the second branch flow path extend in a direction perpendicular to an axis of the throttle portion. 請求項１に記載の冷媒分流器において、
前記冷媒衝突面は、前記絞り部の下流端部から当該絞り部の軸線の延長線上に配置され、
前記第１分流路及び前記第２分流路の上流端は、前記冷媒攪拌室の壁面において前記絞り部の下流端部と前記冷媒衝突面との間に開口していることを特徴とする冷媒分流器。 The refrigerant flow divider according to claim 1,
The refrigerant collision surface is arranged on an extension line of the axis of the throttle part from the downstream end of the throttle part,
The upstream ends of the first branch channel and the second branch channel are opened between the downstream end of the constriction section and the refrigerant collision surface on the wall surface of the refrigerant stirring chamber. vessel. 請求項２に記載の冷媒分流器において、
前記第１分流路及び前記第２分流路の上流端は、前記絞り部の下流端部と前記冷媒衝突面との間の中央部よりも前記絞り部に近い側に開口していることを特徴とする冷媒分流器。 The refrigerant flow divider according to claim 2,
The upstream ends of the first branch channel and the second branch channel are characterized in that they open closer to the throttle section than the center between the downstream end of the throttle section and the refrigerant collision surface. Refrigerant flow divider. 請求項２または３に記載の冷媒分流器において、
前記第１分流路及び前記第２分流路の上流端は、前記冷媒攪拌室の壁面において前記延長線まわりに互いに間隔をあけて配置されていることを特徴とする冷媒分流器。 The refrigerant flow divider according to claim 2 or 3,
The refrigerant flow divider characterized in that the upstream ends of the first branch flow channel and the second branch flow channel are arranged at intervals from each other around the extension line on the wall surface of the refrigerant stirring chamber. 請求項１から４のいずれか１つに記載の冷媒分流器において、
前記供給路及び前記絞り部が設けられた第１分流器構成部材と、
前記冷媒攪拌室、前記冷媒衝突面、前記第１分流路及び前記第２分流路が設けられた第２分流器構成部材とを備え、
前記第１分流器構成部材は、内部に前記絞り部が設けられ、先端面に前記絞り部の下流端が開口する突出筒部を有し、
前記第２分流器構成部材は、前記突出筒部が嵌合する嵌合孔を有し、前記冷媒攪拌室は、前記嵌合孔の奥側に連通するように設けられていることを特徴とする冷媒分流器。 The refrigerant flow divider according to any one of claims 1 to 4,
a first flow divider component provided with the supply path and the constriction part;
a second flow divider component in which the refrigerant stirring chamber, the refrigerant collision surface, the first branch flow path, and the second flow branch are provided;
The first flow divider component has the constriction part provided therein, and a protruding cylindrical part having a downstream end of the constriction part opened at the distal end surface,
The second flow divider component has a fitting hole into which the protruding cylindrical portion fits, and the refrigerant stirring chamber is provided so as to communicate with a back side of the fitting hole. refrigerant flow divider. 請求項５に記載の冷媒分流器において、
前記嵌合孔の径は、前記冷媒攪拌室の径よりも大きく設定されていることを特徴とする冷媒分流器。 The refrigerant flow divider according to claim 5,
A refrigerant flow divider characterized in that a diameter of the fitting hole is set larger than a diameter of the refrigerant stirring chamber. 請求項１から６のいずれか１つに記載の冷媒分流器において、
前記供給路は、前記絞り部の軸線の延長線と交差する方向に延びていることを特徴とする冷媒分流器。 The refrigerant flow divider according to any one of claims 1 to 6,
The refrigerant flow divider, wherein the supply path extends in a direction intersecting an extension of the axis of the throttle section. 請求項１から６のいずれか１つに記載の冷媒分流器において、
前記供給路は、前記絞り部の軸線の延長線と略同軸上に延びていることを特徴とする冷媒分流器。 The refrigerant flow divider according to any one of claims 1 to 6,
The refrigerant flow divider characterized in that the supply path extends substantially coaxially with an extension of the axis of the throttle portion. 請求項１から８のいずれか１つに記載の冷媒分流器において、
前記冷媒衝突面は、円形状とされ、
前記絞り部の下流端部は、当該絞り部の軸線の延長線が前記冷媒衝突面の中心を通るように配置されていることを特徴とする冷媒分流器。 The refrigerant flow divider according to any one of claims 1 to 8,
The refrigerant collision surface has a circular shape,
The refrigerant flow divider is characterized in that the downstream end of the throttle part is arranged such that an extension of the axis of the throttle part passes through the center of the refrigerant collision surface. 請求項９に記載の冷媒分流器において、
前記冷媒衝突面と前記絞り部の軸線の延長線とが略直交していることを特徴とする冷媒分流器。 The refrigerant flow divider according to claim 9,
A refrigerant flow divider characterized in that the refrigerant collision surface and an extension of the axis of the throttle portion are substantially perpendicular to each other.
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Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014081149A (en) 2012-10-17 2014-05-08 Hitachi Appliances Inc Refrigerant distributor and refrigeration cycle device including the same

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2182664A (en) * 1936-12-17 1939-12-05 Gen Electric Refrigerant distributor for cooling units
JPS5920610Y2 (en) * 1980-09-20 1984-06-15 ダイキン工業株式会社 Refrigeration equipment flow divider
JPH07294061A (en) * 1994-04-28 1995-11-10 Sharp Corp Refrigerant distributor
JPH08296778A (en) * 1995-04-25 1996-11-12 Nippondenso Co Ltd Piping connector
JPH09159320A (en) * 1995-12-05 1997-06-20 Matsushita Electric Ind Co Ltd Refrigerant distributor
JPH11257801A (en) * 1998-03-16 1999-09-24 Daikin Ind Ltd Refrigerant distributor
JP4560939B2 (en) * 2000-10-20 2010-10-13 ダイキン工業株式会社 Refrigerant shunt and air conditioner using the same
CN101466986A (en) * 2006-06-29 2009-06-24 大金工业株式会社 Expansion valve with refrigerant flow dividing structure and refrigeration unit utilizing the same
DE102007028565A1 (en) * 2007-06-19 2008-12-24 Danfoss A/S refrigeration Equipment
JP2009002557A (en) * 2007-06-20 2009-01-08 Daikin Ind Ltd Refrigerant flow divider and refrigerating device
KR101424263B1 (en) * 2007-09-21 2014-07-31 엘지전자 주식회사 air-conditioner
KR101547353B1 (en) * 2008-11-10 2015-08-25 엘지전자 주식회사 Distributor and refrigerant circulation system comprising the same
JP6667070B2 (en) * 2016-07-19 2020-03-18 パナソニックＩｐマネジメント株式会社 Refrigerant flow divider and refrigeration system using the same
CN106705513A (en) * 2017-01-12 2017-05-24 青岛海尔空调器有限总公司 Air conditioner and distributor thereof

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014081149A (en) 2012-10-17 2014-05-08 Hitachi Appliances Inc Refrigerant distributor and refrigeration cycle device including the same

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