WO1991002931A1 - Diviseur d'ecoulement pour refrigerant - Google Patents

Diviseur d'ecoulement pour refrigerant Download PDF

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Publication number
WO1991002931A1
WO1991002931A1 PCT/JP1990/001005 JP9001005W WO9102931A1 WO 1991002931 A1 WO1991002931 A1 WO 1991002931A1 JP 9001005 W JP9001005 W JP 9001005W WO 9102931 A1 WO9102931 A1 WO 9102931A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
pipe
wall
inflow
flow divider
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP1990/001005
Other languages
English (en)
Japanese (ja)
Inventor
Shinichi Ide
Teruhiko Taira
Koichi Nakayama
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP1213329A external-priority patent/JP2746681B2/ja
Priority claimed from JP1213330A external-priority patent/JP2820443B2/ja
Application filed by Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Priority to KR1019910700369A priority Critical patent/KR920701766A/ko
Publication of WO1991002931A1 publication Critical patent/WO1991002931A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • 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

Definitions

  • the present invention relates to a refrigerant diverter for uniformly diverting a refrigerant in a refrigeration cycle of an air conditioner or a refrigeration apparatus.
  • Fig. 1 to Fig. 2 show the shape of a conventional refrigerant flow divider
  • Fig. 3 shows the state of attachment of the refrigerant flow divider to the heat exchanger
  • Fig. 4 shows the heat exchanger.
  • reference numeral 1 denotes a flow divider, an inlet pipe 4 having an inlet 2 and an outlet 3 at the other end, followed by a conical body 5 and a cylindrical body 6. Further, it is constituted by a plurality of outflow pipes 9 having an inflow port 7 and an outflow port 8 at the other end.
  • Reference numeral 10 denotes a refrigerant branch section
  • reference numeral 11 denotes a heat exchanger that forms a refrigerant circuit by a refrigerant pipe 12.
  • the flow divider 1 forms a plurality of refrigerant circuits. Heat exchanger It is attached to the side of 11.
  • the refrigerant A flowing through the refrigeration cycle flows into the heat exchanger 11, it flows into the shunt 1 upstream of the refrigeration cycle, is diverted, and is formed by the refrigerant pipe 12. Flowed into the refrigerant circuit.
  • the refrigerant A flowing from the inlet 2 as a two-phase flow of the gas phase A 1 and the liquid phase A 2 passes through the inlet pipe 4, passes through the conical body 5 and the cylindrical body 6. It passes through the branch 10 and is diverted to a plurality of outlet pipes 9a and 9b, and flows out to the refrigerant pipes 12a and 12b via outlets 8a and 8b, respectively.
  • a part of the refrigerant A does not flow smoothly from the outflow pipes 9a and 9b, and a part of the liquid phase A2 collides with the upper wall surface of the cylindrical body 6, falls and falls, and the conical body 5a.
  • the liquid stays and circulates at the lower part of the cylindrical body 6 to form a liquid reservoir.
  • a part of the gas phase A 1 stays and circulates in the upper part of the cylindrical body 6 to form an air pocket.
  • the refrigerant A flows through the inlet pipe 4 of the flow divider 1
  • the refrigerant A has a non-uniform gas-liquid ratio in its cross section.
  • the liquid has been separated, and this state continues even while passing through the conical cylinder 5 and the cylindrical cylinder 6.
  • the liquid level in the liquid pool is disturbed by the two-phase flow that flows in, and the amount of liquid phase entrained from the liquid level also becomes uneven.
  • the flow divider 1 is installed at an angle to the vertical, the liquid phase A 2 retained in the flow divider 1 flows to the outlet pipe 9 below the vertical direction in a large amount.
  • a first object of the present invention is to accelerate the refrigerant flowing into the inflow portion by squeezing, and to cause the refrigerant to collide with the collision wall, so that the refrigerant in the gaseous state and the liquid phase
  • the refrigerant in the state is mixed sufficiently uniformly with o
  • the second purpose is to make it possible to evenly divert to the outflow pipe by making the liquid spillage in the diversion part and almost eliminating the part where air is generated. It is.
  • the third object is to reduce the size and cost of the conventional refrigerant flow divider by connecting the outlet pipe radially to the peripheral wall of the flow division section.
  • a substantially cylindrical diversion part having an inflow part forming a restriction at one end, and a collision wall at the other end having a collision wall for changing a flow direction from the inflow part; It is composed of a plurality of outflow pipes radially joined to the peripheral wall of the diversion section.
  • FIG. 1 is a perspective view of a conventional refrigerant flow divider
  • Fig. 2 is a cross-sectional view of the refrigerant flow divider shown in Fig. 1
  • Fig. 3 is a heat exchanger of the refrigerant flow divider shown in Fig. 1.
  • FIG. 4 is a perspective view showing the mounting state of the refrigerant
  • FIG. 4 is a cross-sectional view showing the flow of the refrigerant when the refrigerant flow divider shown in FIG. 1 is used
  • FIG. 5 is a first embodiment of the present invention.
  • FIG. 6 is a perspective view of a refrigerant flow divider in an example
  • FIG. 6 is a cross-sectional view of the refrigerant flow divider shown in FIG.
  • FIG. 7 is a second embodiment of the present invention.
  • Perspective of refrigerant flow divider Fig. 8, Fig. 8 is a sectional view of the refrigerant flow divider shown in Fig. 7
  • Fig. 9 is a perspective view of the refrigerant flow divider according to the third embodiment of the present invention
  • Fig. 10 is Fig. 9
  • FIG. 11 is a cross-sectional view of the refrigerant flow divider shown in FIG. 11
  • FIG. 11 is a cross-sectional view showing the flow of the refrigerant in use of the refrigerant flow divider shown in FIG. 9,
  • FIG. 13 is a perspective view of the refrigerant flow divider shown in FIG. 12, FIG.
  • FIG. 13 is a cross-sectional view of the refrigerant flow divider shown in FIG. 12, and FIG. 14 is a refrigerant flow divider shown in FIG.
  • FIG. 15 is a cross-sectional view showing the flow of the refrigerant in the use state of FIG. 15,
  • FIG. 15 is a perspective view of the refrigerant flow divider according to the fifth embodiment of the present invention
  • FIG. 17 is a cross-sectional view of the refrigerant flow divider, and FIG. 17 is a cross-sectional view showing the flow of the refrigerant when the refrigerant flow divider shown in FIG. 15 is in use.
  • FIG. 5 shows the appearance of the refrigerant flow divider according to the first embodiment of the present invention in use
  • FIG. 6 shows a cross-sectional view thereof
  • FIG. 7 shows a second embodiment of the present invention
  • FIG. 8 shows a sectional view of the second embodiment.
  • 22 and 22' denote inlet portions forming a throttle
  • Collision walls arranged opposite to 22 and 22 ', 24 and 24' are substantially cylindrical diversion parts
  • Reference numerals 28 and 28 'de note inlet pipes that are installed during actual use.
  • the refrigerant flowing through the refrigerant flow divider 21 is in a two-phase flow of a gas phase 26 and a liquid phase 27, enters through an inlet 22 forming a throttle, and flows out of an outlet pipe 25. It diverts to and exits.
  • the two-phase flow in which the gas phase 26 and the liquid phase 27 exist unevenly in the part of the inflow pipe 28 before flowing into the refrigerant flow divider 21 1 forms a restriction. As they pass through the inlet 22, they are mixed and the flow is accelerated.
  • the two-phase flow obtains a sufficiently uniform mixing state, spreads radially along the collision wall 23, and forms a substantially cylindrical branch portion 2. It is diverted to an outflow pipe 25 radially joined to the peripheral wall of No. 4.
  • the mixed state of the refrigerant is limited to the gas phase 2 due to the restriction and the collision. 6, liquid phase 27
  • the mixing effect keeps the mixture uniform, so that it is evenly diverted.
  • outflow pipe 25 is radially connected to the peripheral wall of the substantially cylindrical diversion section 24, so that the size and the cost of the conventional refrigerant diversion apparatus 21 are reduced. Is possible. In particular, in the second embodiment, the size can be significantly reduced.
  • the inflow portions 22 and 22 'forming a throttle at one end and the inflow portions 22 and 22 at the other end are provided.
  • a substantially cylindrical diversion part having collision walls 23, 23 ′ for changing the direction of the flow from 2 ′, and a substantially cylindrical diversion part 24, 24 ′ By comprising a plurality of outflow pipes 25, 25 'radially joined, it is possible to realize even diversion, and at the same time, to achieve miniaturization and low cost reduction. You can do it.
  • FIGS. 9 to 10 show the shapes of the refrigerant flow dividers according to the third embodiment of the present invention.
  • FIG. 11 shows a case where the heat exchanger was operated in a refrigeration cycle.
  • reference numeral 31 denotes a refrigerant flow divider, which is a small-sized blower for ejecting the refrigerant toward the substantially hemispherical collision wall 32 at one end and the collision wall 32 at the other end. It is composed of a diversion part 35 provided with an inflow pipe 34 having a hole 33, and a plurality of outflow pipes 36 radially arranged on the wall surface of the diversion part 35. .
  • the outflow pipe mounting hole 37 of the diversion section 35 is erected and the outflow pipe 36 is fitted outside the erection process.
  • the maximum distance from the small hole 33 of the inflow pipe 34 to the deepest part of the collision wall 32 is the maximum distance from the pipe wall of the outflow pipe 36 to the deepest part of the collision wall 32.
  • the inflow pipe 34 is fitted to the inflow port of the diversion section 35 so as to be shorter.
  • Refrigerant B flowing through the refrigeration cycle forms a two-phase flow of gas phase B 1 and liquid phase B 2, passes through inlet hole 34, passes through small hole 33, and flows into refrigerant flow divider 31. You At this time, the two-phase flow becomes a jet in which the gas phase B1 and the liquid phase B2 are mixed by the narrowing action of the small holes 33. Thereafter, the jetted refrigerant collides with the substantially hemispherical collision wall 32 facing the air, and further gas-liquid mixing is performed by the collision mixing effect.
  • the inside of the refrigerant flow divider 31 becomes a state in which gas-liquid is uniformly mixed.
  • the homogenized refrigerant B spreads radially along the substantially hemispherical collision wall 32, and branches and flows out to the outlet pipe 36 attached to the branch part 35.
  • the volume inside the refrigerant flow divider 3 1 is small. Therefore, liquid pools and air pockets are rarely formed inside the refrigerant flow divider 31.
  • the refrigerant B is equally divided and flows out to the outflow pipe 36 while the gas and liquid are uniformly mixed.
  • the collision wall 32 is substantially hemispherical, the outlet pipe mounting hole 37 is edged, and the outlet pipe 36 is processed outside the erecting process. For this reason, the refrigerant B is equally divided and flows out without any obstacle from the collision to the outflow.
  • the inlet pipe 34 is provided with the small hole 33, the collision wall 32 for receiving the outflow jet is made hemispherical, and the refrigerant flow divider is provided.
  • the two phases of the refrigerant B inside the refrigerant flow divider 3 1 are mixed and uniform, and this uniform state is maintained.
  • the distance from the small hole 33 of the inflow pipe 34 to the deepest part of the collision wall 32 is the maximum value of the distance from the pipe wall of the outflow pipe 36 to the deepest part of the collision wall 32. Since the inflow pipe 34 is fitted to the inflow port of the diversion section 35 so as to be shorter, the impingement wall 3 2 extends from the small hole 3 3 of the inflow pipe 34. Due to the long distance, the flow velocity of the refrigerant in the branching section 35 decreases, and a liquid pool near the small hole 33 in the branching section 35 occurs. Attachment of the inflow pipe 34 at the inlet of the flow dividing section 35 can be distorted, and the refrigerant can be prevented from directly flowing into one of the outflow pipes 36.
  • FIGS. 12 to 13 show the shapes of the refrigerant flow dividers according to the fourth embodiment of the present invention
  • FIG. 14 shows a case where the heat exchanger is operated in a refrigeration cycle. This shows the state of the refrigerant inside the refrigerant flow divider at the time.
  • reference numeral 41 denotes a refrigerant flow divider, which is an inlet pipe 44 having an inlet 42 and a small hole 43 at the other end, and a jet from the small hole 43.
  • the receiving collision wall 45, the surrounding wall 46 surrounding it, a plurality of outflow pipes 49 having an inflow hole 47 with a smaller inner diameter and an outflow port 8 at the other end are divided by refrigerant.
  • the refrigerant B flowing through the closed circuit of the refrigeration cycle flows into the refrigerant flow divider 41 from the inlet 42 as a two-phase flow of the gas phase B1 and the liquid phase B2. After passing through the inflow pipe 4 4, it gushes out of the small hole 4 3. At this time, the two-phase flow described above is contracted and accelerated by the nozzle action and flows out as a jet. Thereafter, the jet of the refrigerant B collides with the top collision wall 45 and is stirred and mixed. Due to the collision, stirring, and mixing actions, the mixing state of the gas-liquid two-phase flow of the refrigerant B is made uniform.
  • the homogenized refrigerant B radially spreads along the top collision wall 45 and flows out and flows into the inlet 47 of the outflow pipe 49 attached to the peripheral wall 46.
  • the gas-liquid mixed state of the refrigerant B was not changed. Is uniformed by the nozzle effect, and the inner diameter of the inlet 47 is narrowed, so that the uniformed two-phase flow is ejected by the throttle effect. Therefore, the branch flow to each outlet pipe 49 is equalized.
  • the inlet pipe 44 is provided with the small hole 43, and the small hole 43 is received by the collision wall 45 and the peripheral wall 46 receiving the outflow jet.
  • FIG. 15 shows an external view of the refrigerant flow divider according to the embodiment of the present invention
  • FIG. 16 shows a sectional view thereof
  • Fig. 17 shows the state of the refrigerant inside the refrigerant flow divider when the heat exchanger is used as an evaporator during refrigeration cycle operation.
  • 51 is a refrigerant flow divider
  • 52 is a cylindrical flow branch
  • the flow branch 52 is a collision wall 53 at one end
  • a refrigerant flows into the other end.
  • the mouth 54 and the surrounding wall are provided with a plurality of outlets 55.
  • the coolant inlet 54 has a curved portion 56a and the coolant flows out.-
  • the small hole 56c at the end and the narrowed portion 56b near the small hole 56c are provided.
  • An inflow pipe 56 is connected to the outflow port 55, and an outflow pipe 57 is connected to the outflow port 55.
  • the refrigerant B flowing through the closed circuit of the refrigeration cycle passes through the inflow pipe 56 as a two-phase flow of the liquid phase B1 and the gas phase B2.
  • the liquid phase B1 and the gaseous phase B2 undergo gas-liquid separation in an uneven state due to the influence of gravity g and the curved portion 56, and are deflected. ing . That After that, the refrigerant B is accelerated by contraction and acceleration by the constriction section 56b to become a jet, and the liquid phase B1 and the gaseous phase B2 are mixed and the drift is improved. From c, it gushes to the diversion section 52.
  • the refrigerant 17 is contracted and accelerated again by the nozzle effect, and flows out as a jet, collides with the collision wall 53, and is agitated and mixed. Due to the collision, agitation, and mixing, the mixed state of the refrigerant B gas-liquid two-phase flow is completely homogenized.
  • the uniformed refrigerant B spreads radially along the collision wall 56, flows out of the plurality of outlets 55 of the peripheral wall of the branch part 52 into the outlet pipe 57, and the branching is completed.
  • the mixed state of the air flow of the cooling medium B remains uniform by the above-described nozzle effect and collision effect.
  • the refrigerant B is equally distributed.
  • the cylindrical shape having one end serving as the collision wall 56 and having a sufficiently small content so that the liquid pool and the air pool are not generated.
  • the gravity g and the curved part 56a are reduced.
  • An inflow pipe 56 that can reduce the drift caused by the influence and uniformly mix and flow the gas and liquid into the diversion section 52, and an outflow pipe 57 in the peripheral wall of the diversion section 52 with the provision of (1) and (2), even when the refrigerant flow divider 51 is installed in any state, the refrigerant can be equally distributed. Further, in the present embodiment, one narrowing portion 56b of the inflow pipe 56 is provided, but the same effect can be obtained even if a plurality of narrowing portions 56b are provided. It goes without saying.
  • a substantially cylindrical shape having an inflow portion forming a constriction at one end and a collision wall at the other end for changing the direction of flow from the inflow portion.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Branch Pipes, Bends, And The Like (AREA)

Abstract

L'invention se rapporte à un diviseur d'écoulement comprenant une partie d'admission d'écoulement (22) présentant un étranglement à l'une de ses extrémités, une partie de division d'écoulement à peu près cylindrique (24) comportant une paroi de butée d'écoulement (23) servant à changer la direction de l'écoulement provenant de la partie d'admission (22), ainsi que plusieurs tubes de sortie (25) reliés à la paroi périphérique de la partie de division d'écoulement (24) et disposés dans le sens radial, de sorte que la phase gazeuse du réfrigérant s'écoulant dans la partie d'admission (22) soit mélangée uniformément avec sa phase liquide, pour permettre une division uniforme de sa quantité. Grâce à l'agencement des tuyaux de sortie (25) reliés à la paroi périphérique de la partie de division d'écoulement à peu près cylindrique (24) selon une disposition radiale, on peut réduire la taille du diviseur d'écoulement ainsi que son coût de fabrication.
PCT/JP1990/001005 1989-02-21 1990-08-06 Diviseur d'ecoulement pour refrigerant Ceased WO1991002931A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1019910700369A KR920701766A (ko) 1989-02-21 1990-08-06 냉매분류기

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP1213329A JP2746681B2 (ja) 1989-08-18 1989-08-18 冷媒分流器
JP1213330A JP2820443B2 (ja) 1989-08-18 1989-08-18 分流器
JP1/213329 1989-08-18
JP1/213330 1989-08-18

Publications (1)

Publication Number Publication Date
WO1991002931A1 true WO1991002931A1 (fr) 1991-03-07

Family

ID=26519733

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1990/001005 Ceased WO1991002931A1 (fr) 1989-02-21 1990-08-06 Diviseur d'ecoulement pour refrigerant

Country Status (2)

Country Link
MY (1) MY107315A (fr)
WO (1) WO1991002931A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007003087A (ja) * 2005-06-23 2007-01-11 Matsushita Electric Ind Co Ltd 分岐チャンバーおよび換気装置
CN106705513A (zh) * 2017-01-12 2017-05-24 青岛海尔空调器有限总公司 空调及其分液器
CN106705500A (zh) * 2015-11-12 2017-05-24 浙江万享科技股份有限公司 蒸发器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5150017A (ja) * 1974-10-28 1976-05-01 Sadayoshi Yamazaki Ikeikan
JPS51100364U (fr) * 1975-02-12 1976-08-12
JPS52129053U (fr) * 1976-03-29 1977-10-01
JPS5460347U (fr) * 1977-10-05 1979-04-26
JPS5980665U (ja) * 1982-11-25 1984-05-31 三菱電機株式会社 空気調和機の分配器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5150017A (ja) * 1974-10-28 1976-05-01 Sadayoshi Yamazaki Ikeikan
JPS51100364U (fr) * 1975-02-12 1976-08-12
JPS52129053U (fr) * 1976-03-29 1977-10-01
JPS5460347U (fr) * 1977-10-05 1979-04-26
JPS5980665U (ja) * 1982-11-25 1984-05-31 三菱電機株式会社 空気調和機の分配器

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007003087A (ja) * 2005-06-23 2007-01-11 Matsushita Electric Ind Co Ltd 分岐チャンバーおよび換気装置
CN106705500A (zh) * 2015-11-12 2017-05-24 浙江万享科技股份有限公司 蒸发器
CN106705513A (zh) * 2017-01-12 2017-05-24 青岛海尔空调器有限总公司 空调及其分液器

Also Published As

Publication number Publication date
MY107315A (en) 1995-11-30

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