WO2017072833A1 - 冷媒分配器、及びそれを用いた空気調和機 - Google Patents
冷媒分配器、及びそれを用いた空気調和機 Download PDFInfo
- Publication number
- WO2017072833A1 WO2017072833A1 PCT/JP2015/080113 JP2015080113W WO2017072833A1 WO 2017072833 A1 WO2017072833 A1 WO 2017072833A1 JP 2015080113 W JP2015080113 W JP 2015080113W WO 2017072833 A1 WO2017072833 A1 WO 2017072833A1
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- WIPO (PCT)
- Prior art keywords
- refrigerant
- pipe
- introduction pipe
- refrigerant distributor
- branch
- Prior art date
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Classifications
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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
- 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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- 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
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/028—Evaporators having distributing means
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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
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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
Definitions
- the present invention relates to a refrigerant distributor that distributes refrigerant to a plurality of indoor units, and an air conditioner using the refrigerant distributor.
- an air conditioner uses a refrigeration cycle in which a compressor, a condenser, an expansion valve, and an evaporator are connected in order through a refrigerant pipe.
- the low-pressure gas refrigerant sucked into the compressor is compressed to a predetermined high-pressure and then led to a condenser to exchange heat with air to become a high-pressure liquid refrigerant.
- This high-pressure liquid refrigerant is expanded by being led to an expansion valve, then becomes a low-pressure gas-liquid two-phase refrigerant, sent to the evaporator, exchanges heat with air to become low-pressure gas, and is sucked into the compressor and compressed again. And circulates through the refrigeration cycle described above.
- the refrigerant introduced into the indoor unit having an evaporator is in a gas-liquid two-phase state or a liquid-phase state. Even distribution to the machine is important in maintaining the performance of the heat exchanger.
- a refrigerant distributor that evenly distributes the refrigerant to each branch pipe is provided by providing notches on the end faces of the plurality of branch pipes inserted into the introduction pipes through which the refrigerant circulates and receiving the refrigerant through which the notches circulate. It has been proposed (see, for example, Patent Document 1).
- one end of the adjusting pipe is connected and the other end of the adjusting pipe is closed at the connection portion between the refrigerant pipe and the shunt pipe.
- a refrigerant distributor in which the refrigerant is stirred at the other end where the adjustment pipe is blocked and the refrigerant flowing through the branch pipe is made substantially uniform (see, for example, Patent Document 2).
- the refrigerant is agitated by the adjusting pipe, but the branch pipe through which the refrigerant flows thereafter branches in the vertical direction. For this reason, due to the density of the refrigerant, there is a problem that the gas-phase refrigerant flows upward and the liquid-phase refrigerant easily flows downward, and it is difficult to evenly distribute the refrigerant. In addition, since the distribution amount of the refrigerant changes depending on the inclination of the adjusting pipe, it is difficult to manage the manufacture of the refrigerant distributor, and there is a problem in that quality is likely to vary in the manufacturing process.
- the present invention has been made against the background of the above problems, and an object of the present invention is to obtain a refrigerant distributor that can evenly distribute the refrigerant to a plurality of indoor units, and an air conditioner using the refrigerant distributor.
- the refrigerant distributor according to the present invention includes a first introduction pipe that opens at one end and closes the other end, and circulates the refrigerant from one end to the other end, Both ends on the downstream side are closed, a second introduction pipe that circulates the refrigerant in a direction opposite to the refrigerant flow direction of the first introduction pipe, and the refrigerant distribution direction of the second introduction pipe in order A plurality of connected branch pipes, and an adjustment pipe connecting the first introduction pipe and the second introduction pipe, wherein the adjustment pipe is the other of the first introduction pipes
- the end portion side is connected between the upstream end portion of the second introduction pipe and the branch pipe connected to the most upstream side of the second introduction pipe.
- the refrigerant distributor includes the adjustment pipe, and the adjustment pipe is connected to the other end side of the first introduction pipe, the upstream end of the second introduction pipe, and the second introduction pipe. It is set as the structure connected between the branch pipes connected to the most upstream side. In this way, the centrifugal force when the refrigerant flows from the first introduction pipe to the second introduction pipe can be canceled and the refrigerant can be agitated, so that the refrigerant is evenly distributed to the plurality of indoor units.
- a refrigerant distributor that can be used, and an air conditioner using the refrigerant distributor can be obtained.
- FIG. 1 is a schematic perspective view of a refrigerant branching unit equipped with a refrigerant distributor according to Embodiment 1 of the present invention. It is a schematic side view of the refrigerant distributor according to Embodiment 1 of the present invention. 1 is a schematic perspective view of a refrigerant distributor according to Embodiment 1 of the present invention. It is a schematic top view of the refrigerant distributor according to Embodiment 1 of the present invention. It is an expansion schematic perspective view of the lower end part of the refrigerant distributor which concerns on Embodiment 1 of this invention. It is a figure which shows the quantity of the liquid refrigerant
- FIG. 1 is a circuit diagram of an air conditioner equipped with a refrigerant distributor according to Embodiment 1 of the present invention.
- the air conditioner 100 includes one outdoor unit 30, six indoor units 40a, indoor units 40b, indoor units 40c, indoor units 40d, indoor units 40e, and indoor units 40f.
- the outdoor unit 30 includes a compressor 31, a four-way valve 32, an outdoor heat exchanger 33, a refrigerant distributor 20, an outdoor expansion valve 21a, an outdoor expansion valve 21b, an outdoor expansion valve 21c, an outdoor expansion valve 21d, an outdoor expansion valve 21e, An outdoor expansion valve 21f and a gas branch header 35 are sequentially connected by a refrigerant pipe.
- An outdoor fan 34 is disposed in the vicinity of the outdoor heat exchanger 33.
- the four-way valve 32 may not be provided.
- the outdoor heat exchanger 33 corresponds to the “condenser” in the present invention.
- indoor units 40a to 40f will be referred to as indoor units 40 unless otherwise distinguished.
- outdoor expansion valves 21a to 21f are referred to as outdoor expansion valves 21 unless otherwise distinguished.
- the indoor units 40a to 40f are branched from the refrigerant distributor 20 via the refrigerant pipe and provided in parallel to the outdoor unit 30.
- the indoor units 40a to 40f are connected to the gas branch header 35 through refrigerant piping.
- the indoor units 40a to 40f are provided with indoor heat exchangers 41a to 41f, respectively. Note that the indoor heat exchangers 41a to 41f are referred to as indoor heat exchangers 41 unless otherwise distinguished.
- the indoor heat exchanger 41 corresponds to the “evaporator” in the present invention.
- the high-pressure gas refrigerant compressed by the compressor 31 passes through the four-way valve 32 and flows into the outdoor heat exchanger 33.
- the high-pressure gas refrigerant that has flowed into the outdoor heat exchanger 33 is cooled by exchanging heat with outdoor air by the outdoor fan 34, and is condensed to become high-pressure liquid refrigerant.
- the high-pressure liquid refrigerant that has flowed out of the outdoor heat exchanger 33 is decompressed by the outdoor expansion valve 21 and becomes a low-pressure gas-liquid two-phase refrigerant.
- the gas-liquid two-phase refrigerant is distributed to each indoor unit 40 by the refrigerant distributor 20 and flows into each indoor heat exchanger 41.
- the gas-liquid two-phase refrigerant that has flowed into each indoor unit 40 evaporates by exchanging heat with room air, and becomes a low-pressure gas refrigerant.
- the low-pressure gas refrigerant is collected by the gas branch header 35, sent to the compressor via the four-way valve 32, and circulates again through the refrigerant circuit.
- the gas branch header 35 may be a conventional product and may not have special technical features.
- FIG. 2 is a schematic front view of a conventional refrigerant branching unit.
- FIG. 3 is a schematic perspective view of a conventional refrigerant branching unit.
- FIG. 4 is a schematic side view of a refrigerant distributor provided in a conventional refrigerant branching unit.
- FIG. 5 is a schematic perspective view of a refrigerant distributor provided in a conventional refrigerant branching unit.
- FIG. 6 is a schematic top view of a conventional refrigerant distributor.
- the conventional refrigerant branching unit 70 includes a refrigerant distributor 71 that distributes liquid refrigerant and a gas branch header 72 that branches gas refrigerant.
- the refrigerant distributor 71 includes a U-shaped introduction pipe 75 that includes an introduction pipe 73 that circulates the refrigerant from top to bottom and an introduction pipe 74 that circulates the refrigerant from bottom to top. Connected through.
- a branch pipe 76a, a branch pipe 76b, a branch pipe 76c, a branch pipe 76d, a branch pipe 76e, and a branch pipe 76f for distributing the refrigerant to each indoor unit are respectively separated at predetermined intervals.
- the conventional refrigerant distributor 71 causes the refrigerant to flow from the top to the bottom of the introduction pipe 73 and flows into the introduction pipe 74 from the bottom to the top through the U-shaped introduction pipe 75.
- the refrigerant flowing into the introduction pipe 74 is branched and distributed to the branch pipe 76a, the branch pipe 76b, the branch pipe 76c, the branch pipe 76d, the branch pipe 76e, and the branch pipe 76f, respectively.
- FIG. 7 is a diagram showing the amount of liquid refrigerant distributed to each branch pipe in a conventional refrigerant distributor.
- FIG. 7 the liquid refrigerant is distributed in the order of the branch pipe 76f, the branch pipe 76e, the branch pipe 76d, the branch pipe 76c, the branch pipe 76b, and the branch pipe 76a. That is, the amount of liquid-phase refrigerant increases in the branch pipe provided above the introduction pipe 74, and almost no liquid-phase refrigerant is distributed to the branch pipe provided below.
- the reason why the amount of the lower branch pipe is smaller than that of the upper branch pipe is that the centrifugal force exerted on the liquid refrigerant generated in the U-shaped introduction pipe 75 has an effect, and this centrifugal force causes a biased liquid phase refrigerant. Is caused by the warp flowing through the inlet of the branch pipe.
- the branch pipe is installed in the centrifugal direction, that is, the direction in which the liquid-phase refrigerant is biased, and the amount of the liquid-phase refrigerant flowing into each branch pipe is analyzed.
- the branch provided above the introduction pipe 74 is analyzed.
- the amount of the liquid-phase refrigerant increased as the pipe increased, and almost no liquid-phase refrigerant was distributed to the branch pipe provided below. This is because the flow rate of the liquid-phase refrigerant is increased due to the centrifugal force, and the refrigerant is less likely to flow into the lower branch pipe that passes in a state where the speed of the liquid-phase refrigerant is high.
- FIG. 8 is a schematic perspective view of a refrigerant branching unit equipped with the refrigerant distributor according to Embodiment 1 of the present invention.
- FIG. 9 is a schematic side view of the refrigerant distributor according to Embodiment 1 of the present invention.
- FIG. 10 is a schematic perspective view of the refrigerant distributor according to Embodiment 1 of the present invention.
- FIG. 11 is a schematic top view of the refrigerant distributor according to Embodiment 1 of the present invention.
- the refrigerant branching unit 80 includes a refrigerant distributor 20 that distributes the liquid refrigerant and a gas branch header 35 that branches the gas refrigerant.
- the refrigerant distributor 20 includes a first introduction pipe 12 that circulates refrigerant from top to bottom and a second introduction pipe 11 that circulates refrigerant from bottom to top. It is connected via the U-shaped adjustment pipe 13 in the state of viewing.
- the first introduction pipe 12 is disposed in a vertical direction in a horizontal and flat place, the upper end 12a is opened, the lower end 12b is closed, and the refrigerant is circulated from top to bottom.
- both the lower end portion 11b on the upstream side and the upper end portion 11a on the downstream side are closed, and the refrigerant is passed from below. Distribute on top.
- the arrows in the figure indicate the refrigerant flow 15.
- the upper end portion 12a corresponds to “one end portion” in the present invention.
- the lower end 12b corresponds to the “other end” in the present invention.
- the second introduction pipe 11 and the first introduction pipe 12 are pipes having an outer diameter of 12.0 (mm) and a thickness of 0.7 (mm), for example.
- the adjustment pipe 13 is, for example, a U-shaped pipe having an outer diameter of 9.52 (mm) and a wall thickness of 0.7 (mm) when viewed from above.
- the inner diameter of the adjustment pipe 13 to be smaller than the inner diameters of the second introduction pipe 11 and the first introduction pipe 12, the flow rate of the refrigerant can be adjusted by the adjustment pipe 13 even when the circulation amount of the refrigerant is small.
- the gas-liquid two-phase refrigerant can be sufficiently stirred at the time of flowing into the second introduction pipe 11 with sufficient security.
- specific numerical values are shown for the dimensions of the second introduction pipe 11, the first introduction pipe 12 and the adjustment pipe 13, but the present invention is not limited to this. The dimensions may be appropriately changed depending on the scale of the conditioner 100 or the type of refrigerant.
- a branch pipe 10a, a branch pipe 10b, a branch pipe 10c, a branch pipe 10d, a branch pipe 10e, and a branch pipe 10f for distributing the refrigerant to each indoor unit are spaced apart from each other by a predetermined interval. Connected along the flow direction of the refrigerant.
- the branch pipe is provided at the lowest position of the branch pipe 10a, and the second introduction is performed so that the branch pipe 10a, the branch pipe 10b, the branch pipe 10c, the branch pipe 10d, the branch pipe 10e, and the branch pipe 10f increase in this order. It is installed in the tube 11.
- an example is shown in which six branch pipes 10a to 10f are connected to the second introduction pipe 11.
- branch pipes 10a to 10f will be referred to as branch pipes 10 unless particularly distinguished.
- an outdoor expansion valve 21 is provided on the downstream side of the branch pipe 10.
- FIG. 12 is an enlarged schematic perspective view of the lower end portion of the refrigerant distributor according to Embodiment 1 of the present invention.
- the adjustment pipe 13 is connected to the first introduction pipe 12 via the connection portion 13a.
- tube 13 is connected to the 2nd introduction pipe 11 via the connection part 13b. That is, the adjusting pipe 13 is branched at the lower end 12 b side of the first introduction pipe 12 to the lower end 11 b on the upstream side of the second introduction pipe 11 and the most upstream side of the second introduction pipe 11. It connects between the pipe
- the adjustment pipe 13 is installed at an angle of 90 ° with respect to the second introduction pipe 11 and the first introduction pipe 12.
- the adjustment pipe 13 is inserted in an airtight manner through a connection portion 13b opened to the second introduction pipe 11, and is inserted in an airtight manner through a connection section 13a opened to the first introduction pipe 12. For this reason, it is necessary to design the outer diameter of the adjustment pipe 13 to be smaller than the outer diameters of the second introduction pipe 11 and the first introduction pipe 12. Moreover, the adjustment pipe
- tube 13 is installed in the position of height 25 (mm) from the lower end part 11b and the lower end part 12b.
- tube 13 showed the example installed in the position of height 25 (mm) from the lower end part 11b and the lower end part 12b
- this invention is not limited to this, The height may be changed as appropriate depending on the scale of the air conditioner 100 or the type of refrigerant.
- the example in which the height of the lower end part 11b and the lower end part 12b was equal in FIG. 12 was shown, the height of the lower end part 11b and the lower end part 12b may be different from each other. The same applies to the second to third embodiments described later.
- the gas-liquid two-phase refrigerant that has been sufficiently stirred and the centrifugal force canceled is circulated toward the upper side of the second introduction pipe 11 and is distributed to each branch pipe 10.
- the refrigerant distributor 20 has one end opened and the other end closed, and the refrigerant flows from one end to the other end.
- the first introduction pipe 12, the both ends of the upstream side and the downstream side are closed, the second introduction pipe 11 that circulates the refrigerant in the direction opposite to the refrigerant flow direction of the first introduction pipe, and the second
- the inlet pipe 11 has a plurality of branch pipes 10 connected in the refrigerant flow direction, and an adjustment pipe 13 that connects the first introduction pipe 12 and the second introduction pipe 11.
- the other end side of the first introduction pipe 12 is between the upstream end of the second introduction pipe 11 and the branch pipe 10 connected to the most upstream side of the second introduction pipe 11. Connected.
- the adjusting tube 13 has a diameter smaller than the inner diameters of the first introduction tube 12 and the second introduction tube 11.
- the adjusting tube 13 is U-shaped when viewed from above.
- coolant distribution which can collide the refrigerant
- a container 20 can be obtained.
- the adjustment pipe 13 is installed perpendicular to the first introduction pipe 12 and the second introduction pipe 11.
- the air conditioner 100 includes a refrigeration cycle configured by connecting a compressor 31, an outdoor heat exchanger 33, a plurality of outdoor expansion valves 21 and a plurality of indoor heat exchangers 41 in order by refrigerant piping, A refrigerant distributor 20 is provided between the outdoor heat exchanger 33 and the plurality of outdoor expansion valves 21. By doing in this way, the air conditioner 100 provided with the refrigerant distributor 20 which can distribute a gas-liquid two-phase refrigerant
- FIG. 14 is an enlarged schematic perspective view of the lower end portion of the refrigerant distributor according to Embodiment 2 of the present invention.
- the refrigerant distributor 20 a includes an adjustment pipe 17, a first introduction pipe 12, and a second introduction pipe 11.
- the adjustment tube 17 is U-shaped when viewed from above.
- the adjustment pipe 17 is connected to the first introduction pipe 12 via the connection portion 13a, and is connected to the second introduction pipe 11 via the connection portion 13b.
- the adjustment pipe 17 is in relation to the first introduction pipe 12 and the second introduction pipe 11. It is connected to the branch pipe 10 at an angle. That is, the adjustment pipe 17 is inclined upward and connected to the first introduction pipe 12 and the second introduction pipe 11.
- the gas-liquid two-phase refrigerant that has been sufficiently stirred and the centrifugal force canceled is circulated toward the upper side of the second introduction pipe 11 and is distributed to each branch pipe 10.
- the adjustment pipe 17 is provided to be inclined toward the branch pipe 10 side.
- the centrifugal force applied to the gas-liquid two-phase refrigerant is canceled, the flow velocity is reduced, and the gas-liquid two-phase refrigerant is added after sufficiently stirring.
- Embodiment 3 Since the basic configuration of the refrigerant distributor according to the third embodiment is the same as that of the refrigerant distributor according to the first embodiment, the third embodiment will be described below with a focus on differences from the first embodiment. .
- the difference between the first embodiment and the third embodiment is that the adjustment tube has a linear shape.
- FIG. 15 is an enlarged schematic perspective view of the lower end portion of the refrigerant distributor according to Embodiment 3 of the present invention.
- the refrigerant distributor 20 b includes an adjustment pipe 16, a first introduction pipe 12, and a second introduction pipe 11.
- the adjustment tube 16 has a linear shape when viewed from above.
- the adjustment pipe 16 is connected to the first introduction pipe 12 via the connection portion 13a, and is connected to the second introduction pipe 11 via the connection portion 13b.
- the adjustment pipe 16 is horizontal to the first introduction pipe 12 and the second introduction pipe 11. It is connected to the.
- connection part 13a of the first introduction pipe 12 may be provided at a position higher than the connection part 13b of the second introduction pipe 11, and the adjustment pipe 16 may be installed inclined.
- the refrigerant that has flowed out of the adjustment pipe 16 collides more with the lower end portion 11b of the second introduction pipe 11, so that the gas-liquid two-phase refrigerant is further stirred and the flow rate of the refrigerant is reduced.
- the gas-liquid two-phase refrigerant is decelerated by colliding with the inner wall surface and the lower end portion 11b of the second introduction pipe 11, and the gas-liquid two-phase refrigerant is agitated by the impact at the time of the collision. Is further promoted.
- the gas-liquid two-phase refrigerant that has been sufficiently agitated flows upward above the second introduction pipe 11 and is distributed to each branch pipe 10.
- the flow rate of the gas-liquid two-phase refrigerant is reduced, and after sufficient stirring, the gas-liquid two-phase refrigerant is distributed to each branch pipe 10 to supply a homogeneous refrigerant to each distributor. It becomes possible.
- the adjustment tube 16 has a linear shape when viewed from above.
- distributor 20b which can reduce the flow velocity of a refrigerant
- coolant can be obtained.
- the adjustment pipe 16 is connected to a position where the connection part 13a on the first introduction pipe 12 side is higher than the connection part 13b on the second introduction pipe 11 side.
Abstract
Description
[空気調和機の構成]
図1は、本発明の実施の形態1に係る冷媒分配器を搭載した空気調和機の回路図である。図1に示されるように、空気調和機100は、1台の室外機30と、6台の室内機40a、室内機40b、室内機40c、室内機40d、室内機40e、室内機40fとを備える。室外機30には、圧縮機31、四方弁32、室外熱交換器33、冷媒分配器20、室外膨張弁21a、室外膨張弁21b、室外膨張弁21c、室外膨張弁21d、室外膨張弁21e、室外膨張弁21f、ガス分岐ヘッダー35が冷媒配管により順次接続され設けられている。また室外熱交換器33の近傍には、室外ファン34が配置されている。空気調和機100が冷房専用の機種の場合には、四方弁32を設けなくてもよい。なお、室外熱交換器33は、本発明における「凝縮器」に相当する。
次に、冷房運転における冷媒の流れについて説明する。圧縮機31で圧縮された高圧ガス冷媒は、四方弁32を通り、室外熱交換器33に流入する。室外熱交換器33に流入した高圧ガス冷媒は、室外ファン34によって室外空気と熱交換をすることで冷却され、凝縮して高圧液冷媒となる。室外熱交換器33から流出した高圧液冷媒は、室外膨張弁21で減圧されて低圧の気液二相状態の冷媒となる。この気液二相の冷媒は、冷媒分配器20によって各室内機40に分配され、各室内熱交換器41に流入する。各室内機40に流入した気液二相の冷媒は、室内空気と熱交換を行うことで蒸発し、低圧ガス冷媒となる。この低圧ガス冷媒は、ガス分岐ヘッダー35で集約され、四方弁32を経由して圧縮機へ送られ、再び冷媒回路を循環する。なお、ガス分岐ヘッダー35は従来品でよく、特別な技術的特徴を有していなくてもよい。
本実施の形態1に係る冷媒分配器の説明の前に、まず従来の冷媒分配器について説明する。
図2は、従来の冷媒分岐ユニットの概略正面図である。また、図3は、従来の冷媒分岐ユニットの概略斜視図である。また、図4は、従来の冷媒分岐ユニットに備えられている冷媒分配器の概略側面図である。また、図5は、従来の冷媒分岐ユニットに備えられている冷媒分配器の概略斜視図である。また、図6は、従来の冷媒分配器の概略上面図である。
次に、本実施の形態1に係る冷媒分配器について説明する。図8は、本発明の実施の形態1に係る冷媒分配器を搭載した冷媒分岐ユニットの概略斜視図である。また、図9は、本発明の実施の形態1に係る冷媒分配器の概略側面図である。また、図10は、本発明の実施の形態1に係る冷媒分配器の概略斜視図である。また、図11は、本発明の実施の形態1に係る冷媒分配器の概略上面図である。
図12は、本発明の実施の形態1に係る冷媒分配器の下端部の拡大概略斜視図である。図12に示されるように、調整管13は接続部13aを介して第一の導入管12に接続されている。また、調整管13は接続部13bを介して第二の導入管11に接続されている。すなわち、調整管13は、第一の導入管12の下端部12b側を、第二の導入管11の上流側の下端部11bと第二の導入管11の最上流側に接続されている分岐管10aとの間に接続している。調整管13は、第二の導入管11及び第一の導入管12に対して、90°の角度で設置されている。
次に、冷媒分配器20内での冷媒の挙動について説明する。
図12に示されるように、第一の導入管12の上方から下方へ流入する気液二相の冷媒は、第一の導入管12の下端部12bの内壁面に衝突し、下方へ向かう勢いが打ち消されると共に、気相冷媒と液相冷媒が攪拌される。そして、気液二相の冷媒は、接続部13aから調整管13へ流入する。調整管13はU字形状をなしているため気液二相の冷媒には遠心力が加わる。接続部13bを介して調整管13を流出した気液二相の冷媒は、第二の導入管11に流入する。この際、気液二相の冷媒は、第二の導入管11の内壁面及び下端部11bの内壁面に衝突することで遠心力が打ち消されると共に流速が減速させられ、さらに衝突した際の衝撃で気液二相の冷媒の攪拌が一層促進される。攪拌が十分に行われ遠心力が打ち消された気液二相の冷媒は、第二の導入管11の上方に向かって流通し、各分岐管10に分配される。このように、気液二相の冷媒に加わる遠心力を打ち消し、冷媒の流速を減速させ、攪拌を十分に行った後に気液二相の冷媒を各分岐管10に分配することで、各分配器に均質な冷媒を供給することが可能となる。
以上のことから、本実施の形態1によれば、冷媒分配器20は、一方の端部が開口し他方の端部が閉口し、一方の端部から他方の端部の方向に冷媒を流通する第一の導入管12と、上流側及び下流側の両端部が閉口し、第一の導入管の冷媒の流通方向と逆方向に冷媒を流通する第二の導入管11と、第二の導入管11の冷媒の流通方向に接続された複数本の分岐管10と、第一の導入管12と第二の導入管11とを接続する調整管13と、を有し、調整管13は、第一の導入管12の他方の端部側を、第二の導入管11の上流側の端部と第二の導入管11の最上流側に接続されている分岐管10との間に接続している。このようにすることで、気液二相冷媒を複数の室内機40に均等に分配できる冷媒分配器20を得ることができる。
本実施の形態2における冷媒分配器の基本的な構成は実施の形態1における冷媒分配器と同様であるため、以下、実施の形態1との相違点を中心に本実施の形態2を説明する。実施の形態1と本実施の形態2との相違点は、調整管が第一の導入管及び第二の導入管に対して傾いている点である。
次に、冷媒分配器20a内での冷媒の挙動について説明する。
図14に示されるように、第一の導入管12の上方から下方へ流入する気液二相の冷媒は、第一の導入管12の下端部12bの内壁面に衝突し、下方へ向かう勢いが打ち消されると共に、気相冷媒と液相冷媒が攪拌される。そして、気液二相の冷媒は、接続部13aから調整管17へ流入する。調整管17はU字形状をなしているため気液二相の冷媒には遠心力が加わる。接続部13bを介して調整管13を流出した気液二相の冷媒は、第二の導入管11に流入する。この際、気液二相の冷媒は、第二の導入管11の内壁面及び下端部11bの内壁面に衝突することで遠心力が打ち消されると共に流速が減速させられ、さらに衝突した際の衝撃で気液二相の冷媒の攪拌が一層促進される。攪拌が十分に行われ遠心力が打ち消された気液二相の冷媒は、第二の導入管11の上方に向かって流通し、各分岐管10に分配される。このように、気液二相の冷媒に加わる遠心力を打ち消すと共に流速を減速させ、さらに攪拌を十分に行った後に気液二相の冷媒を各分岐管10に分配することで、各分配器に均質な冷媒を供給することが可能となる。
以上のことから、本実施の形態2によれば、調整管17は、分岐管10側に傾いて設けられている。このようにすることで、実施の形態1の効果に加えて、気液二相の冷媒に加わる遠心力を打ち消すと共に流速を減速させ、さらに攪拌を十分に行った後に気液二相の冷媒を各分岐管10に分配することで、各分配器に均質な冷媒を供給することが可能となる。
本実施の形態3における冷媒分配器の基本的な構成は実施の形態1における冷媒分配器と同様であるため、以下、実施の形態1との相違点を中心に本実施の形態3を説明する。実施の形態1と本実施の形態3との相違点は、調整管が直線形状である点である。
次に、冷媒分配器20b内での冷媒の挙動について説明する。
図15に示されるように、第一の導入管12の上方から下方へ流入する気液二相の冷媒は、第一の導入管12の下端部12bの内壁面に衝突し、下方へ向かう勢いが打ち消されると共に、気相冷媒と液相冷媒が攪拌される。そして、気液二相の冷媒は、接続部13aから調整管16へ流入する。接続部13bを介して調整管16を流出した気液二相の冷媒は、第二の導入管11に流入する。この際、気液二相の冷媒は、第二の導入管11の内壁面及び下端部11bに衝突することで流速が減速させられ、さらに衝突した際の衝撃で気液二相の冷媒の攪拌が一層促進される。攪拌が十分に行われた気液二相の冷媒は、第二の導入管11の上方に向かって流通し、各分岐管10に分配される。このように、気液二相の冷媒の流速を減速させ、攪拌を十分に行った後に気液二相の冷媒を各分岐管10に分配することで、各分配器に均質な冷媒を供給することが可能となる。
以上のことから、本実施の形態3によれば、調整管16は、上面視した状態において直線形状である。このようにすることで、実施の形態1の効果に加えて、冷媒の流速を減速させ、尚且つ気液二相の冷媒の攪拌を促進することができる冷媒分配器20bを得ることができる。
Claims (10)
- 一方の端部が開口し他方の端部が閉口し、一方の端部から他方の端部の方向に冷媒を流通する第一の導入管と、
上流側及び下流側の両端部が閉口し、前記第一の導入管の冷媒の流通方向と逆方向に冷媒を流通する第二の導入管と、
前記第二の導入管の冷媒の流通方向に沿って順に接続された複数本の分岐管と、
前記第一の導入管と前記第二の導入管とを接続する調整管と、を有し、
前記調整管は、
前記第一の導入管の前記他方の端部側を、前記第二の導入管の上流側の端部と前記第二の導入管の最上流側に接続されている前記分岐管との間に接続している
冷媒分配器。 - 前記第一の導入管は、
鉛直方向に配置された場合において、上方から下方へ冷媒を流通させ、
前記第二の導入管は、
鉛直方向に配置された場合において、下方から上方へ冷媒を流通させる
請求項1に記載の冷媒分配器。 - 前記調整管は、
前記第一の導入管及び前記第二の導入管の内径よりも小さい径を有している
請求項1又は2に記載の冷媒分配器。 - 前記調整管は、
上面視した状態においてU字形状である
請求項1~3のいずれか一項に記載の冷媒分配器。 - 前記調整管は、
前記第一の導入管及び前記第二の導入管に対して垂直に設置されている
請求項4に記載の冷媒分配器。 - 前記調整管は、
前記分岐管側に傾いている
請求項4に記載の冷媒分配器。 - 前記調整管は、
上面視した状態において直線形状である
請求項1~3のいずれか一項に記載の冷媒分配器。 - 前記調整管は、
前記第一の導入管側の接続部が前記第二の導入管側の接続部より高い位置に接続されている
請求項7に記載の冷媒分配器。 - 圧縮機、凝縮器、複数の室外膨張弁及び複数の蒸発器を順に冷媒配管により接続して構成される冷凍サイクルを備えた空気調和機であって、
前記凝縮器と前記複数の室外膨張弁との間に、請求項1~8の何れか一項に記載の冷媒分配器を備えた空気調和機。 - 前記圧縮機、前記凝縮器、前記複数の室外膨張弁、及び前記冷媒分配器が1台の室外機に搭載された
請求項9に記載の空気調和機。
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US15/763,145 US10712062B2 (en) | 2015-10-26 | 2015-10-26 | Refrigerant distributor and air-conditioning apparatus using the same |
CN201580084141.9A CN108351133B (zh) | 2015-10-26 | 2015-10-26 | 制冷剂分配器以及使用制冷剂分配器的空调机 |
EP15907197.6A EP3370020B1 (en) | 2015-10-26 | 2015-10-26 | Refrigerant distributor, and air conditioner using same |
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