CN101097104A - Gas-liquid two-phase liquid distributor - Google Patents

Gas-liquid two-phase liquid distributor Download PDF

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Publication number
CN101097104A
CN101097104A CNA200710109516XA CN200710109516A CN101097104A CN 101097104 A CN101097104 A CN 101097104A CN A200710109516X A CNA200710109516X A CN A200710109516XA CN 200710109516 A CN200710109516 A CN 200710109516A CN 101097104 A CN101097104 A CN 101097104A
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CN
China
Prior art keywords
distributor
liquid
gas
hydrostatic column
phase
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.)
Granted
Application number
CNA200710109516XA
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Chinese (zh)
Other versions
CN101097104B (en
Inventor
大村源太郎
西岛春幸
山田悦久
武内裕嗣
松井秀也
藤原良子
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.)
Denso Corp
Original Assignee
Denso Corp
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Publication date
Application filed by Denso Corp filed Critical Denso Corp
Publication of CN101097104A publication Critical patent/CN101097104A/en
Application granted granted Critical
Publication of CN101097104B publication Critical patent/CN101097104B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • 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
    • F25B41/45—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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high pressure
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Cyclones (AREA)
  • Jet Pumps And Other Pumps (AREA)

Abstract

A distributor able to evenly supply influent two-phase refrigerant flowing in by various flow states to different pipes with an extremely small pressure loss, that is, a distributor of a gas-liquid two-phase fluid distributing a gas-liquid two-phase fluid flowing in from an inlet pipe into a plurality of distribution pipes, provided with a cylindrical vessel with a cylindrical upper part, an inlet pipe connected in a tangential direction with respect to a circular cross section of the upper portion of the cylindrical vessel, and distribution pipes connected to a lower portion of the cylindrical vessel.

Description

Gas-liquid two-phase flow body distributor
Technical field
The present invention relates to a kind of distributor, described distributor is set in the refrigerant loop of air-conditioning system etc., and two phase refrigerant is distributed to a plurality of heat exchangers etc., specifically, the present invention relates to the structure that the uniform two phase refrigerant of blending ratio is evenly separated.
Background technology
As shown in Figure 4, in the past, kind of refrigeration cycle 100 was proposed, this kind of refrigeration cycle 100 is in turn connected into annular by refrigerant tubing 107 with first refrigerant evaporator 113 and the gas-liquid separator 106 of coolant compressor 102, refrigerant condenser 103, injector 104, indoor heat converter 105, and the bypass duct 109 of second refrigerant evaporator 114 by being provided with indoor heat converter 105 couples together (No. the 3265649th, Japan Patent) with the suction portion 108 of the liquid phase refrigerant side of gas-liquid separator 106 and injector 104.
Here, as shown in Figure 5, injector 4 is attached on the side surface of indoor heat converter 105.As shown in Figure 6, injector 4 sprays the liquid phase refrigerant of cooled dose of condenser 103 condensations and liquefaction, vapor phase refrigerant is inhaled into portion's 108 suctions thus, liquid phase refrigerant and vapor phase refrigerant be mixed and pressure rising in diffuser 111, then the cold-producing medium of solution-air two-phase state (below, be called as " two phase refrigerant ") is transported in first refrigerant evaporator 113 by distributor 112.As illustrated in fig. 1 and 2, distributor 112 is such pipes, and the cold-producing medium of the solution-air two-phase state that it will flow out from injector 104 is assigned to a plurality of conduits of first refrigerant evaporator 113 equably.
The effect of distributor 112 be with different flow regimes (slag stream, mist flow, annular flow, or the like) two phase refrigerant that flows into is supplied to pipe equably.However, but the cold-producing medium that nozzle 110 sprays, and it flows and is subjected to the influence of solution-air ratio and flow velocity.The cold-producing medium that liquid phase is many flows through distributing pipe 112a down under the effect of gravity, and the many cold-producing mediums of gas phase flow through distributing pipe 112b.Therefore, distributor 112 can not be realized its effect fully.
In addition, in the downstream of injector the pressure loss takes place, the boosting of injector is reduced.Therefore, should avoid the pressure loss in injector downstream as far as possible.However, because cold-producing medium directly flows to distributing pipe 112 from diffuser 111, it changes to such direction, is reduced greatly along described direction cross sectional area.Because this throttle effect, the pressure loss has taken place.Should be noted that well-known, circulation is compared with injector, in the expansion valve circulation, the pressure loss amount at dispenser portion place is regulated by the amount of restriction of expansion valve, so pressure loss effect is very little.
On the other hand, as the distributor of two phase refrigerant, in Japan Patent open (A) 6-201225 number and 5-340648 number, disclose some, but these distributors all there is energy loss, because for the transmission of solution-air after separating, they upwards promote liquid.In addition, these distributors need the downstream rounded upper surface, and its diameter is greater than the diameter of vortex part (swirl part), and need the conical surface of slight inclination so that keep liquid film, so become great unpractical container.The both can not ideally carry out its function.
Summary of the invention
A target of the present invention provides a kind of distributor, and described distributor can not have to be supplied to pipe under the situation of the pressure loss equably to the two phase refrigerant that the state flow that flows with difference is gone into.
According to the aspect that the present invention comprised, the invention provides a kind of gas-liquid two-phase flow body distributor, as the device of realizing above-mentioned target.
According to a first aspect of the invention, provide a kind of gas-liquid two-phase flow body distributor, described distributor is provided with hydrostatic column, and described hydrostatic column has: cylindrical upper section; Inlet tube, described inlet tube tangentially is connected with respect to the circular cross-section on the top of described hydrostatic column; And distributing pipe, described distributing pipe is connected to the bottom of described hydrostatic column.
Because inlet tube tangentially is connected with respect to the circular cross-section of hydrostatic column, under known centrifugation, the form of tube inlet stream is not how, and two-phase fluid is separated into gas phase and liquid phase in described hydrostatic column.Described liquid phase forms thin liquid film at the inner surface place of described hydrostatic column, and drips under the effect of gravity, and the effect along with cold-producing medium vortex stream forms uniform liquid film thickness.The liquid film that forms with uniform thickness flows downward in vortex, and arrives a plurality of distributing pipes that are arranged on place, hydrostatic column bottom.In described distributing pipe, the liquid film and the vapor phase refrigerant that form with uniform thickness flow into, so, mix evenly that the two-phase fluid of forming forms and mobile by gas and liquid.In addition, two-phase fluid is moving in described container under the gravity effect, so energy loss (pressure loss) is minimum.
According to a second aspect of the invention, in gas-liquid two-phase flow body distributor, the bottom of hydrostatic column forms back taper.Two-phase fluid forms vortex stream along the inner surface of described container, and flows to the container bottom under the gravity effect.At this moment, the lip-deep liquid film of back taper that occurs because of centrifugation is subjected to force component upwards with respect to this centrifugal force owing to back taper is surperficial, so falling speed is slowed down.In addition, because the back taper surface, angular velocity omega increases, centrifugal force mr ω 2Become big, and promoted centrifugation (because peripheral speed is constant basically because of the amount that radius r diminishes).Therefore, the uniform more liquid film of thickness falls in the time of vortex on described back taper surface.
According to a third aspect of the invention we, provide as the described distributor of first aspect, wherein, described inlet tube was bent before being connected to described hydrostatic column just.Described bend has the function that causes centrifugation, so can make the hydrostatic column that produces centrifugation littler.
According to a forth aspect of the invention, provide a kind of kind of refrigeration cycle, described kind of refrigeration cycle is provided with any distributor in the above-mentioned distributor in the downstream of injector.
Description of drawings
These and other objects of the present invention and feature will be from becoming clearer the description of preferred embodiments in conjunction with the accompanying drawings subsequently, wherein:
Fig. 1 shows first embodiment of distributor of the present invention with schematic diagram;
Fig. 2 shows second embodiment of distributor of the present invention with schematic diagram;
Fig. 3 shows the 3rd embodiment of distributor of the present invention with schematic diagram;
Fig. 4 shows the traditional kind of refrigeration cycle that is provided with injector;
Fig. 5 is the perspective view of indoor heat converter that forms the part circulation of Fig. 4; And
Fig. 6 shows the injector and the distributor of the part circulation that forms Fig. 4.
Specific embodiment
Describe the preferred embodiments of the present invention below with reference to accompanying drawings in detail.
First embodiment
Fig. 1 shows first embodiment of distributor of the present invention with schematic diagram.Fig. 1 (a) shows the vertical view of described distributor, and Fig. 1 (b) shows the sectional view of described distributor simultaneously.Among Fig. 1, Reference numeral 10 is distributors of first embodiment, the 1st, and hydrostatic column, the 2nd, inlet tube, the 3rd, distributing pipe.
Inlet tube 2 tangentially is connected with respect to the circular cross-section on hydrostatic column 1 top.At the place, bottom of hydrostatic column 1, a plurality of distributing pipes 3 are connected the edge circumferentially with equal angles position spaced place, and extend radially outward.In other words, a plurality of distributing pipes 3 are connected on the hydrostatic column 1, make that the interval between them becomes equidistant.
In addition, the gas phase two phase refrigerant (for example, liquid phase approximately is 0.3 volume % with the ratio of gas phase) tangential direction from inlet tube 2 along the peripheral part office flows into the hydrostatic column 1, and, in the process of hydrostatic column 1 inner vortex (swirl), described gas phase two phase refrigerant is separated into gas and liquid by effect centrifugal force thereon.Heavy liquid is collected at the outer circumferential side place, and light gas is collected in the center simultaneously.Gas becomes uniform pressure, and flows to distributing pipe 3 from outlet 3a in vortex in moving process.
On the other hand, described liquid is along the inner surface vortex of cylindrical wall 1a, and free-falling under the gravity effect, vortex, and form liquid film.Along with the carrying out of this process, because capillary effect, the thickness of liquid film becomes homogeneous thickness on whole circumference, and flows into distributing pipe 3.Should be noted that when the volume ratio of liquid phase was 0.3 volume %, the thickness of liquid film was about 0.1mm.The liquid free-falling does not but have energy loss so can move downward.
Like this, when flowing into distributing pipe 3, near distributing pipe 3, liquid becomes the uniform film of thickness on whole circumference, and gas becomes uniform pressure on whole circumference.Therefore, the gas phase two phase refrigerant can be by uniform distribution.On the contrary, if make the interval of distributing pipe 3 installation sites unequal, then can change the ratio that is assigned to distributing pipe 3.
Second embodiment
Fig. 2 shows the lateral section of second embodiment of distributor of the present invention by schematic diagram.Vertical view is identical with Fig. 1 (a), so be omitted.The distributor of second embodiment only is that hydrostatic column is different with first embodiment.Therefore, identical with the parts of first embodiment basically parts have been assigned with identical Reference numeral, and omit explanation.
Among Fig. 2, Reference numeral 20 is distributors of second embodiment, and 21 is the containers (being called " top hydrostatic column " below) with cylindrical upper section 21b and back taper bottom 21c simultaneously.
Two phase refrigerant forms vortex stream along the inner surface 21a of container 21, and flows to the bottom of container 21.At this moment, the liquid film that is produced by centrifugation on the back taper surface is subjected to force component upwards, should be applied with respect to this centrifugal force by back taper surface 21c by force component upwards, so falling speed is slowed down.In addition, because the back taper surface, angular velocity omega increases, and has promoted centrifugation.Therefore, in the time of vortex on the back taper surface, the more uniform liquid film of thickness falls.
Should be noted that near the diameter D2 of the circular cross-section of (that is, the distributing pipe connecting portion) is more preferably greater than inlet tube inside diameter D 1 near taper-cut summit (cut apex).This is for fear of losing because of the throttle effect build-up of pressure.In addition, the angle of inclination of described taper can be by being configured to optimal value as the flow velocity at container entrance place, the mass dryness fraction of cold-producing medium, the parameter of D1, D2 or the like and so on.
Like this, near distributing pipe 3, when flowing into distributing pipe 3, liquid forms thickness film more uniformly on whole circumference, and gas becomes uniform pressure on whole circumference simultaneously.Therefore, the gas phase two phase refrigerant can be distributed equably.
The 3rd embodiment
Fig. 3 shows the vertical view of the 3rd embodiment of distributor of the present invention with schematic diagram.Sectional view is identical with Fig. 1 (b), so be omitted.The distributor of the 3rd embodiment only is that inlet tube is different with first embodiment.Therefore, identical with the first embodiment parts basically parts have been assigned with identical Reference numeral, and omit explanation.
Among Fig. 2, Reference numeral 30 is distributors of the 3rd embodiment, and 32 is inlet tubes simultaneously.Inlet tube 32 has bend 32a, and described bend 32a just was bent before being connected to hydrostatic column 1.This bend 32a has the function that produces centrifugation, measures accordingly so hydrostatic column 1 is diminished.
Although selected specific embodiment has been described the present invention with reference to illustrating for example, yet obviously those skilled in the art can make change to these embodiment under the situation that does not break away from basic design of the present invention and protection domain.

Claims (4)

1. gas-liquid two-phase flow body distributor, described distributor will be assigned to a plurality of distributing pipes from the gas-liquid two-phase flow body that inlet tube flows into, and described distributor is provided with:
Hydrostatic column, described hydrostatic column has cylindrical upper section;
Inlet tube, described inlet tube tangentially is connected with respect to the circular cross-section on the top of described hydrostatic column; And
Distributing pipe, described distributing pipe is connected to the bottom of described hydrostatic column.
2. distributor as claimed in claim 1, wherein, the bottom of described hydrostatic column forms back taper.
3. distributor as claimed in claim 1, wherein, described inlet tube was bent before being connected to described hydrostatic column just.
4. kind of refrigeration cycle, described kind of refrigeration cycle is provided with distributor as claimed in claim 1 in the downstream of injector.
CN200710109516XA 2006-06-30 2007-06-27 Gas-liquid two-phase liquid distributor Expired - Fee Related CN101097104B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2006182386 2006-06-30
JP2006-182386 2006-06-30
JP2006182386A JP4609388B2 (en) 2006-06-30 2006-06-30 Gas-liquid two-phase fluid distributor

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CN101097104A true CN101097104A (en) 2008-01-02
CN101097104B CN101097104B (en) 2011-03-30

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US (1) US20080000263A1 (en)
JP (1) JP4609388B2 (en)
CN (1) CN101097104B (en)
DE (1) DE102007029342A1 (en)

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CN102003845A (en) * 2010-09-19 2011-04-06 深圳麦克维尔空调有限公司 Fluid distributor for air heat exchanger of air conditioner
CN102607216A (en) * 2012-03-28 2012-07-25 湖南科技大学 Cyclone refrigerant branching device
CN102859299A (en) * 2010-04-23 2013-01-02 阿拂迈克奎公司 Flow distributor and environment control system provided with the same
CN103206882A (en) * 2013-03-29 2013-07-17 合肥通用机械研究院 Pipe fitting for improving efficiency of evaporator by enabling refrigerant to flow spirally
CN103657492A (en) * 2013-12-09 2014-03-26 云南大红山管道有限公司 Energy-saving efficient self-stirring container
CN106016850A (en) * 2016-07-15 2016-10-12 珠海格力电器股份有限公司 Air conditioner, dry shell and tube evaporator and refrigerant distributor assembly thereof

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JP4832458B2 (en) * 2008-03-13 2011-12-07 株式会社デンソー Vapor compression refrigeration cycle
JP5003665B2 (en) * 2008-04-18 2012-08-15 株式会社デンソー Ejector refrigeration cycle
US10527329B2 (en) 2008-04-18 2020-01-07 Denso Corporation Ejector-type refrigeration cycle device
WO2009128271A1 (en) * 2008-04-18 2009-10-22 株式会社デンソー Ejector-type refrigeration cycle device
CN101907376B (en) * 2009-06-02 2012-07-25 江森自控楼宇设备科技(无锡)有限公司 Device for distributing refrigerant in refrigeration system
JP4894942B2 (en) * 2009-06-12 2012-03-14 ダイキン工業株式会社 Divider, expansion valve provided with the diverter, and refrigeration apparatus provided with the expansion valve
US8434324B2 (en) * 2010-04-05 2013-05-07 Denso Corporation Evaporator unit
JP5083390B2 (en) * 2010-08-02 2012-11-28 ダイキン工業株式会社 Refrigerant flow divider, refrigerant flow divider integrated expansion device and refrigeration device
JP5640857B2 (en) * 2011-03-28 2014-12-17 株式会社デンソー Pressure reducing device and refrigeration cycle
US10928101B2 (en) 2011-06-10 2021-02-23 Carrier Corporation Ejector with motive flow swirl
JP5920110B2 (en) 2012-02-02 2016-05-18 株式会社デンソー Ejector
CN103673419B (en) * 2012-09-12 2016-06-01 珠海格力电器股份有限公司 Air conditioner and air conditioner shunt thereof
JP6079552B2 (en) * 2012-11-20 2017-02-15 株式会社デンソー Ejector
JP5999071B2 (en) 2012-12-27 2016-09-28 株式会社デンソー Ejector
JP6119566B2 (en) * 2012-12-27 2017-04-26 株式会社デンソー Ejector
WO2015073106A1 (en) * 2013-11-18 2015-05-21 Carrier Corporation Flash gas bypass evaporator
WO2016056086A1 (en) * 2014-10-08 2016-04-14 三菱電機株式会社 Refrigerant pipe and heat pump device
CN106322807B (en) * 2015-07-03 2021-05-28 开利公司 Ejector heat pump
CN106933268B (en) * 2017-02-28 2018-09-25 中国石油大学(北京) Laboratory steam quality monitoring device, monitoring method and steam drive experimental provision
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FR3081985B1 (en) * 2018-05-31 2020-10-09 Valeo Systemes Thermiques FLUID DISTRIBUTOR, AND CORRESPONDING THERMAL EXCHANGER.
MX2020013183A (en) 2018-06-07 2021-04-13 Amgen Inc Detection assay for protein-polynucleotide conjugates.
CN110260570A (en) * 2019-06-21 2019-09-20 珠海格力电器股份有限公司 Swirl generating piece of flow divider, flow dividing assembly, heat exchanger and air conditioner

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US2084755A (en) * 1935-05-03 1937-06-22 Carrier Corp Refrigerant distributor
US2063380A (en) * 1935-10-18 1936-12-08 Peerless Ice Machine Company Refrigerant distributor
JPS50141331U (en) * 1974-05-10 1975-11-20
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CN102859299A (en) * 2010-04-23 2013-01-02 阿拂迈克奎公司 Flow distributor and environment control system provided with the same
CN102859299B (en) * 2010-04-23 2016-03-02 阿拂迈克奎公司 Fluid distributor and the environmental control system being provided with fluid distributor
CN102003845A (en) * 2010-09-19 2011-04-06 深圳麦克维尔空调有限公司 Fluid distributor for air heat exchanger of air conditioner
CN102607216A (en) * 2012-03-28 2012-07-25 湖南科技大学 Cyclone refrigerant branching device
CN103206882A (en) * 2013-03-29 2013-07-17 合肥通用机械研究院 Pipe fitting for improving efficiency of evaporator by enabling refrigerant to flow spirally
CN103206882B (en) * 2013-03-29 2015-05-20 合肥通用机械研究院 Pipe fitting for improving efficiency of evaporator by enabling refrigerant to flow spirally
CN103657492A (en) * 2013-12-09 2014-03-26 云南大红山管道有限公司 Energy-saving efficient self-stirring container
CN106016850A (en) * 2016-07-15 2016-10-12 珠海格力电器股份有限公司 Air conditioner, dry shell and tube evaporator and refrigerant distributor assembly thereof
CN106016850B (en) * 2016-07-15 2018-05-18 珠海格力电器股份有限公司 Air conditioner, dry shell and tube evaporator and refrigerant distributor assembly thereof

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DE102007029342A1 (en) 2008-01-03
JP2008008599A (en) 2008-01-17
CN101097104B (en) 2011-03-30
JP4609388B2 (en) 2011-01-12
US20080000263A1 (en) 2008-01-03

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Termination date: 20200627