CN104272040A - Coolant distributor, and heat exchanger equipped with coolant distributor - Google Patents

Coolant distributor, and heat exchanger equipped with coolant distributor Download PDF

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Publication number
CN104272040A
CN104272040A CN201280072638.5A CN201280072638A CN104272040A CN 104272040 A CN104272040 A CN 104272040A CN 201280072638 A CN201280072638 A CN 201280072638A CN 104272040 A CN104272040 A CN 104272040A
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CN
China
Prior art keywords
mentioned
chamber
heat exchanger
cold
producing medium
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Granted
Application number
CN201280072638.5A
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Chinese (zh)
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CN104272040B (en
Inventor
松田拓也
石桥晃
李相武
冈崎多佳志
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of CN104272040A publication Critical patent/CN104272040A/en
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Publication of CN104272040B publication Critical patent/CN104272040B/en
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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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0202—Header boxes having their inner space divided by partitions
    • F28F9/0204—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions
    • F28F9/0209—Header boxes having their inner space divided by partitions for elongated header box, e.g. with transversal and longitudinal partitions having only transversal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/044—Condensers with an integrated receiver
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Abstract

A coolant distributor has: a header (10a) positioned so as to be standing in the vertical direction, connected to one end of a plurality of flattened tubes (20) in a heat exchanger (1) that conveys coolant in parallel to the plurality of flattened tubes (20) which are arranged in parallel to one another, and having a configuration in which the interior thereof is partitioned in the parallel direction of the plurality of heat-transmitting tubes (20) by one or more partition plates (11); and a distributor (40) for distributing and conveying the coolant to each of the chambers in the header (10a) partitioned by the partition plates (11).

Description

Refrigerant distributor and possess the heat exchanger of this refrigerant distributor
Technical field
The present invention relates to the heat exchanger of the freezing cycle device be such as installed in for air conditioner etc., the refrigerant distributor that cold-producing medium is distributed and the heat exchanger being possessed to this refrigerant distributor.
Background technology
In the past, the following heat exchanger formed was had: configured with leaving at left and right directions by a pair collector extended at above-below direction, between a pair collector, configure multiple flat tube side by side, by the both ends of multiple heat-exchange tube and a pair header in communication.In this heat exchanger, when using as evaporimeter, because cold-producing medium flows into gas-liquid two-phase flow, so in the collector of entrance side, liquid accumulates at gravity direction, on the other hand, gas accumulation in collector above.Thus, cold-producing medium can not distribute to each flat tube by existence equably, the problem of the performance reduction of heat exchanger.
Therefore, when being used as evaporimeter by heat exchanger, the collector for entrance side requires the function of assignment system cryogen equably.As such refrigerant distributor, in the past, there is following refrigerant distributor: the annular flow path of turning back at above-below direction at collector Inner Constitution, the two-phase flow of refrigerant of inflow is homogenized in collector inner loop, and to multiple heat-transfer pipe each distribute (such as, see patent document 1).
In addition, as the evaporimeter of uniform distribution having sought cold-producing medium, there is following evaporimeter: this evaporimeter has makes a pair collector extended at left and right directions (horizontal direction) configure away from each other and between a pair collector, configure the structure of multiple flat tube side by side, on the collector of entrance side, open compartment of terrain at left and right directions sky and multiple refrigerant inlet is set, cold-producing medium is flowed into (such as, see patent document 2) to collector internal spray from each refrigerant inlet through throttle orifice.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2011-85324 publication (summary, Fig. 1)
Patent document 2: Japanese Unexamined Patent Publication 2000-249428 publication (summary, Fig. 4)
Summary of the invention
Invent problem to be solved
In the structure of patent document 1, although the impartial distribution effects of cold-producing medium to a certain degree can be seen, because multiple heat-transfer pipe is all communicated with in collector inside, so, in collector, be subject to the impact of head difference.Therefore, can not assert that cold-producing medium distribution effects is abundant, require further to improve.
In patent document 2, because collector is flatly arranged, so, not by the impact of head difference.But when being arranged with erecting at above-below direction by collector, there is such problem: the impact being subject to head difference, liquid easily accumulates in downside.
The present invention is the invention made in view of above-mentioned problem, its object is to, provides a kind of impact that can suppress head difference, equably assignment system cryogen refrigerant distributor and possess the heat exchanger of this refrigerant distributor.
In order to solve the means of problem
Refrigerant distributor of the present invention has collector and disperser, described collector has and is connected with one end of above-mentioned multiple heat-transfer pipe of the heat exchanger of the multiple heat-transfer pipes making cold-producing medium flow to side by side to configure side by side, and the structure that inside is separated at the also column direction of above-mentioned multiple heat-transfer pipe by more than one demarcation strip, and arrange with erecting at above-below direction, described disperser makes cold-producing medium flow into distributively to by each of each chamber in the above-mentioned collector of above-mentioned divides.
The effect of invention
According to the present invention, the impact that can suppress head difference can be obtained, equably the refrigerant distributor of assignment system cryogen.When being arranged with erecting at above-below direction by collector, effective especially effect can be obtained.
Accompanying drawing explanation
Fig. 1 is the schematic isometric of the heat exchanger of the refrigerant distributor possessing one embodiment of the present invention.
Fig. 2 is the schematic sectional view of a part for the refrigerant distributor of Fig. 1.
Fig. 3 is the stereogram of the flat tube representing Fig. 1.
Fig. 4 is the figure of the refrigerant loop of the freezing cycle device representing the heat exchanger being suitable for Fig. 1.
Fig. 5 is the figure of other structure example representing refrigerant distributor.
Fig. 6 is the key diagram of the decision principle of the height in each chamber corresponding to wind speed profile.
Detailed description of the invention
Fig. 1 is the schematic isometric of the heat exchanger of the refrigerant distributor possessing one embodiment of the present invention.Fig. 2 is the schematic sectional view of a part for the refrigerant distributor of Fig. 1.In Fig. 1, Fig. 2 and figure described later, the parts of mark same symbol are identical or parts suitable with it, and this is general in description full text.And then the form of the inscape represented in description full text is illustrate eventually, is not limited to the form that these are recorded.
Heat exchanger 1 is the heat exchanger of the parallel type that cold-producing medium is flowed side by side, has and configures with leaving and a pair collector 10 (10a, 10b) arranged with erecting at above-below direction at left and right directions; And configure side by side at above-below direction between a pair collector 10, multiple flat tubes (heat-transfer pipe) 20 that two ends are connected with a pair collector 10.And heat exchanger 1 also has disperser 40 and multiple fin 30.A pair collector 10, flat tube 20 and fin 30 are formed by aluminum or aluminum alloy.Disperser 40 is connected with collector 10a through capillary 50, together form refrigerant distributor with collector 10a.
Fin 30 is that the mutual empty standard width of a room in an old-style house is layered between a pair collector 10 every ground, and the plate-shaped fins that air passes through betwixt, multiple flat tube 20 is through in fin 30.In addition, fin 30 also can need not to be plate-shaped fins.Such as, also can be at above-below direction and the fin etc. of waveform shape that configures of the alternately laminated ground of flat tube 20, in a word, as long as be configured to the fin that air passed through by direction at air.
Flat tube 20, as shown in Figure 3, has the multiple through hole 20a becoming refrigerant flow path.
Collector 10a, its inside is separated at above-below direction by more than one demarcation strip 11, defines multiple chamber 12.Here, 8 chambeies 12 are defined by 7 demarcation strips 11.Each chamber 12 each in, define multiple through hole 13 at above-below direction, flat tube 20 therewith each through hole 13 connects.In addition, each of each chamber 12 is connected with disperser 40 through capillary 50.
Disperser 40, there is in inside the throttle orifice (not shown) flowing of cold-producing medium being carried out to throttling, when heat exchanger 1 is used as evaporimeter, the gas-liquid two-phase flowing into itself is made to flow through throttle orifice, carry out spray-fluidized (homogeneous fluidisation) thus, become easily impartial state of distributing.Here, flowed into distributively to each capillary 50 equably by the cold-producing medium carrying out spray-fluidized, by capillary 50, flow into each of each chamber 12.
Capillary 50, according to crushing in its specification (length, internal diameter) Correctional tube, adjusts the split ratio in each chamber 12 to collector 10a.Here, make following capillary: the specification of whole capillaries 50 is identical, make the cold-producing medium of identical amount flow into each chamber 12.
When manufacturing the heat exchanger 1 of such structure, flat tube 20, fin 30, a pair collector 10 being carried out soldered joint with the state of all assembling simultaneously in stove, then, disperser 40 and each capillary 50 is connected.
Fig. 4 is the figure of the refrigerant loop of the freezing cycle device representing the heat exchanger being suitable for Fig. 1.
Freezing cycle device 60 possess compressor 61, condenser 62, as the expansion valve 63 of decompressor and evaporimeter 64.At least one party as condenser 62 and evaporimeter 64 uses heat exchanger 1.The gas refrigerant of discharging from compressor 61 flow into condenser 62, carries out heat exchange, become high pressure liquid refrigerant and flow out with the air by condenser 62.The high pressure liquid refrigerant flowing out condenser 62 is reduced pressure by expansion valve 63, becomes the gas-liquid two-phase cold-producing medium of low pressure, flow into evaporimeter 64.Flow into the gas-liquid two-phase cold-producing medium of the low pressure of evaporimeter 64 and carry out heat exchange by the air of evaporimeter 64, becoming low-pressure refrigerant gas, again sucked by compressor 61.
Below, with reference to Fig. 1 and Fig. 4, the flowing of the cold-producing medium when being used as evaporimeter by heat exchanger 1 is described.In FIG, solid arrow represents the flowing of cold-producing medium when using as evaporimeter.
From the gas-liquid two-phase flow of refrigerant that expansion valve 63 flows out, first flow into disperser 40, carried out spray-fluidized.Flowed into distributively to each capillary 50 equably by the cold-producing medium carrying out spray-fluidized.The each cold-producing medium that have passed each capillary 50 flows into each chamber 12 of collector 10a respectively.
Here, when not arranging the structure in the past of demarcation strip in collector, because the inner overall connection of collector, so the head difference produced because of gravity is large, easily produces bias current.But, in the present embodiment, demarcation strip 11 is set, by collector 10a interior separation, each cold-producing medium is flow into reduce each chamber 12 of head difference.Therefore, the impact of head difference on each cold-producing medium flowing into each chamber 12 reduces, and each cold-producing medium in each chamber 12 is flowed into distributively to each flat tube 20 be connected with this chamber 12 equably.
Flow into each cold-producing medium of each flat tube 20, move towards collector 10b effluent through the through hole 20a of flat tube 20, collaborate in collector 10b, flow out from outside connecting pipings 14 heat exchanger 1.
Below, with reference to Fig. 1 and Fig. 4, the flowing of cold-producing medium when being used as condenser by heat exchanger 1 is described.In FIG, dash-dot arrows represents the flowing of cold-producing medium when using as condenser.
From compressor 61 effluent air flow of refrigerant, flow in collector 10b, carried out equalization here and distribute, flow into each flat tube 20.When cold-producing medium is gaseous state, distribute because easily impartial, so, do not need the refrigerant distributors such as disperser, make the structure making to flow into directly to collector 10b from compressor 61 effluent air flow of refrigerant.
And, flow into each cold-producing medium of each flat tube 20, move towards collector 10a effluent through the through hole 20a of flat tube 20, flow into each of each chamber 12 of collector 10a.Flow into each cold-producing medium of each of each chamber 12, flow into disperser 40, here collaborate through each capillary 50, heat exchanger 1 is outer to flow out.
As described above according to the present embodiment, when heat exchanger 1 is used as evaporimeter, the two-phase flow of refrigerant flowed into is distributed by disperser 40 equalization, each cold-producing medium having been carried out impartial distribution is flow into sought each chamber 12 reducing head difference.Thus, the impact of head difference on each cold-producing medium flowing into each chamber 12 reduces, and can flow into distributively, can suppress bias current to each flat tube 20 equalization.Therefore, by using the refrigerant distributor with this disperser 40 and collector 10a, the ability of evaporimeter can be played to greatest extent, the heat exchanger effectiveness of the heat exchanger 1 as evaporimeter can be improved.
In addition, the position of demarcation strip 11, can consider that can carry out the impartial head difference distributed decides.By only arranging demarcation strip 11 by necessary bottom line, can reduce costs.
In addition, refrigerant distributor of the present invention and heat exchanger, be not limited to the structure shown in Fig. 1, without departing from the spirit and scope of the invention, such as, can carry out various distortion to implement as following (1) ~ (3).
(1) still can arrange in the cold-producing medium inflow part in each chamber 12 and distribute the bias current suppression component of bias current for suppressing.
As bias current suppression component, as long as the parts distributing bias current can be suppressed, such as, can throttle orifice 70 be set as shown in Figure 5.Throttle orifice 70 is arranged on the connector of capillary 50 in chamber 12, has the through hole 71 of the internal diameter less than the internal diameter of capillary 50.Throttle orifice 70 promotes spray-fluidized by carrying out throttling by through hole 71 to the flowing of the cold-producing medium flowed into from capillary 50.By promoting spray-fluidized in this wise, the distribution to each flat tube 20 in chamber 12 is impartial further, can suppress further to distribute bias current.
(2) also the height (multiple flat tube 20 and the length of column direction) in each chamber 12 can correspondingly be determined with the wind speed profile in heat exchanger 1.
From wind speed air heat exchanger 1 being carried out the Air Blast fan of blowing, may not be even in whole of heat exchanger 1, but there is wind speed profile.Such as, when building combined air conditioners, because arrange Air Blast fan on the top of heat exchanger 1, so compared with bottom, the wind speed on the top of heat exchanger 1 accelerates.When heat exchanger 1 is used as evaporimeter, by the cold-producing medium of the fast part of wind speed compared with the cold-producing medium by the slow part of wind speed, easily carry out gasifying and dry.Therefore, when the refrigerant amount flowing into each chamber 12 is identical, by the cold-producing medium of the fast part of wind speed compared with the cold-producing medium by the slow part of wind speed, aridity uprises, in the refrigerant condition flowing into collector 10b, produce deviation.
If produce deviation like this in refrigerant condition, then the refrigerant condition externally flowed out from outside connecting pipings 14 becomes unstable.Therefore, about the collector 10a part that the flat tube 20 being positioned at the fast part of wind speed connects, the height in chamber 12 is diminished, the flat tube quantity be connected is reduced, so that the heat exchange area in each chamber all diminishes with this chamber 12.Be described particularly in Fig. 6 below.
Fig. 6 is the key diagram of the decision principle of the height in each chamber corresponding to wind speed profile, here, illustrate the wind speed wind speed that is fast, lower side of upper side slow when example.
As shown in Figure 6, the height of the chamber 12B of the lower side that the aspect ratio wind speed of the chamber 12A of the upper side making wind speed fast is slow is little, and the flat tube quantity that the flat tube number ratio be connected with chamber 12A is connected with chamber 12B is few.Thus, the heat exchange area A of 12A side, chamber is less than the heat exchange area B of 12B side, chamber, can say that heat transfer area diminishes.Therefore, the heat exchange amount of essence is roughly the same in heat exchange area A with heat exchange area B, and the refrigerant condition of outlet can be made consistent.
In addition, here, illustrate the refrigerant amount flowing into each chamber 12 identical, make by the height changing chamber 12 example that the refrigerant condition of outlet is consistent, but also can as following.That is, make the height in each chamber 12 identical, change the partition amount flowing into the cold-producing medium in each chamber 12.In the case, can correspondingly to determine the partition amount of the cold-producing medium flowing into each chamber 12 with wind speed profile and to become this to be determined capillary 50 specification (length, internal diameter) by the mode of determined partition amount.Specifically, to be positioned at the partition amount in the chamber 12 of the flat tube 20 of the fast part of wind speed many to connecting, capillary 50 is selected to the mode connecting the partition amount that is positioned at the chamber 12 of the flat tube 20 of the slow part of wind speed few.
(3) in the present embodiment, the example that heat exchanger 1 is overall roughly l shape is illustrated, but, also can do integrally roughly L-shaped, entirety roughly U-shaped, overall substantially rectangular shape.Which kind of shape heat exchanger 1 is made, as long as the actual installation space according to the heat exchanger 1 arranged in the housing of heat exchanger 1 correspondingly determines, actual installation space can be maximally utilised and the shape of actual installation to high-density as long as make.
(4) in the present embodiment, heat-transfer pipe has been made flat tube, but, also can need not to be flat tube, make pipe also passable.
The explanation of symbol
1: heat exchanger; 10: collector; 10a: collector; 10b: collector; 11: demarcation strip; 12: chamber; 12A: chamber; 12B: chamber; 13: through hole; 14: outside connecting pipings; 20: flat tube (heat-transfer pipe); 30: fin; 40: disperser; 50: capillary; 60: freezing cycle device; 61: compressor; 62: condenser; 63: expansion valve; 64: evaporimeter; 70: throttle orifice; 71: through hole; A: heat exchange area; B: heat exchange area.

Claims (7)

1. a refrigerant distributor, is characterized in that, has collector and disperser,
Described collector has and is connected with one end of above-mentioned multiple heat-transfer pipe of the heat exchanger of the multiple heat-transfer pipes making cold-producing medium flow to side by side to configure side by side, and the structure that inside is separated at the also column direction of above-mentioned multiple heat-transfer pipe by more than one demarcation strip, and arrange with erecting at above-below direction
Described disperser makes cold-producing medium flow into distributively to by each of each chamber in the above-mentioned collector of above-mentioned divides.
2. refrigerant distributor as claimed in claim 1, is characterized in that, in the cold-producing medium inflow part of each in above-mentioned each chamber, is provided with the bias current suppression component of the bias current suppressing cold-producing medium.
3. refrigerant distributor as claimed in claim 2, it is characterized in that, above-mentioned bias current suppression component is the throttle orifice flowing of cold-producing medium being carried out to throttling.
4. the refrigerant distributor as described in any one in claims 1 to 3, it is characterized in that, wind speed profile in the position of above-mentioned demarcation strip and above-mentioned heat exchanger correspondingly sets, and with the above-mentioned of the above-mentioned chamber connecting the above-mentioned heat-transfer pipe by the fast part of wind speed and the length of column direction than above-mentioned chamber above-mentioned of the above-mentioned heat-transfer pipe connected by the slow part of wind speed and the length of column direction is short mode sets the position of above-mentioned demarcation strip.
5. the refrigerant distributor as described in any one in claims 1 to 3, it is characterized in that, each through carrying out multiple capillaries of the adjustment of refrigerant flow of above-mentioned disperser is connected with each of above-mentioned each chamber, the wind speed profile flow in the partition amount of the cold-producing medium in above-mentioned each chamber and above-mentioned heat exchanger correspondingly sets, to select above-mentioned multiple capillary to connecting the mode that the partition amount comparison being positioned at the above-mentioned chamber of the above-mentioned heat-transfer pipe of the fast part of wind speed connects the partition amount that is positioned at the above-mentioned chamber of the above-mentioned heat-transfer pipe of the slow part of wind speed many.
6. a heat exchanger, is characterized in that, possesses the refrigerant distributor described in any one in claim 1 to 5.
7. heat exchanger as claimed in claim 6, is characterized in that, the also column direction of above-mentioned multiple heat-transfer pipe is above-below direction, and above-mentioned collector is arranged at above-below direction with erecting, and above-mentioned heat-transfer pipe is the flat tube with the multiple through holes becoming refrigerant flow path.
CN201280072638.5A 2012-04-26 2012-04-26 Refrigerant distributor, possess the heat exchanger of this refrigerant distributor, freezing cycle device and air conditioner Active CN104272040B (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/002860 WO2013160952A1 (en) 2012-04-26 2012-04-26 Coolant distributor, and heat exchanger equipped with coolant distributor

Publications (2)

Publication Number Publication Date
CN104272040A true CN104272040A (en) 2015-01-07
CN104272040B CN104272040B (en) 2016-06-15

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