WO2007094422A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
WO2007094422A1
WO2007094422A1 PCT/JP2007/052760 JP2007052760W WO2007094422A1 WO 2007094422 A1 WO2007094422 A1 WO 2007094422A1 JP 2007052760 W JP2007052760 W JP 2007052760W WO 2007094422 A1 WO2007094422 A1 WO 2007094422A1
Authority
WO
WIPO (PCT)
Prior art keywords
heat exchange
exchange medium
header
tubes
inlet header
Prior art date
Application number
PCT/JP2007/052760
Other languages
English (en)
Japanese (ja)
Inventor
Toru Moriya
Takahide Maezawa
Tadashi Nakabou
Original Assignee
Gac Corporation
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
Application filed by Gac Corporation filed Critical Gac Corporation
Priority to EP07714290A priority Critical patent/EP1985949A1/fr
Priority to JP2008500546A priority patent/JP4866416B2/ja
Priority to US12/279,620 priority patent/US20100314090A1/en
Publication of WO2007094422A1 publication Critical patent/WO2007094422A1/fr

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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
    • 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
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure

Definitions

  • the present invention relates to a heat exchanger used in a refrigeration or cooling device.
  • the heat exchange described in this document is provided with refrigerant distribution means using flat distribution pipes, and the flat distribution pipes are concentrated in a part of the header, particularly in the lower part of the header where liquid refrigerant is likely to accumulate. Thus, the liquid refrigerant is caused to flow into the heat exchange part.
  • Such a structure In the case of manufacturing, the refrigerant state at the inlets of multiple flat distribution pipes approaches uniform, but the difference in tube pressure loss due to the difference in tube length occurs, so the refrigerant distribution to multiple tubes is not necessarily uniform. I can not say.
  • it is difficult to provide heat exchange with a simple configuration because it has a structure in which multiple flat distribution pipes with bent parts are arranged.
  • Japanese Patent Publication No. 2000-249428 describes an inlet header, an outlet header, a plurality of tubes extending between both headers, and a meander interposed between adjacent tubes.
  • An evaporator with fins is disclosed.
  • a plurality of refrigerant injectors are provided at the inlet to the inlet header.
  • Each of the plurality of refrigerant injectors has an injection orifice.
  • One aspect of the present invention includes a plurality of tubes, an inlet header for distributing the heat exchange medium to the plurality of tubes, and an outlet header for recovering the heat exchange medium from the plurality of tubes. It has a heat exchanger.
  • the inlet header of the heat exchanger is a circulation pipe through which at least a part of the heat exchange medium flowing into the inlet header can circulate, and a plurality of tubes are connected to at least a part of the circulation pipe.
  • the difference between the generated circulation pipe and the heat exchange medium blown out in the axial direction of the circulation pipe to forcibly circulate at least part of the heat exchange medium flowing into the inlet header through the circulation pipe.
  • a mechanism for generating pressure (differential pressure generating mechanism).
  • the heat exchange medium that has already flowed in
  • the heat exchange medium existing in the inlet header is circulated by the circulation pipe by the differential pressure generation mechanism. It is blown out in the axial direction of the road and circulates forcibly in a circulation pipe line that communicates with multiple tubes. For this reason, the state of the heat exchange medium inside the circulation line constituting the inlet header is more uniform. Or it can be in a nearly uniform state. For example, even when a two-phase heat exchange medium including a gas phase and a liquid phase flows in, the heat exchange medium can be prevented from separating into a liquid phase component and a gas phase component in the inlet header. For this reason, even if a plurality of tubes are connected in an inlet header having a certain axial length and dispersed in the axial direction of the inlet header, a more uniform heat exchange medium is provided for each tube. Can be distributed.
  • this heat exchange ⁇ it is possible to omit a distribution pipe that requires three-dimensional bending. In addition, it is possible to omit bending the tube side in order to make the distribution of the heat exchange medium uniform. This does not exclude the fact that this heat exchange includes these three-dimensional pipes and bent pipes. However, this heat exchange makes it possible to make the phase state and flow rate of the heat exchange medium distributed to each tube uniform or close to that with a simpler configuration. For this reason, a heat exchanger with good heat exchange efficiency can be provided at a relatively low cost.
  • differential pressure generating mechanism is driven by external power such as a pump.
  • Some cooling systems depressurize or expand the heat exchange medium flowing into the heat exchanger in advance.
  • heat exchange applied to such a system it is possible to drive the differential pressure generating mechanism using the energy of the heat exchange medium. In this case, heat exchange
  • the differential pressure generating mechanism is preferably driven by a heat exchange medium flowing into the inlet header.
  • a turbocharger that rotates the turbine with the pressure of the drive part and forcibly sucks the heat exchange medium with the differential pressure generation part (pressurization part) of a coaxial compressor or the like ( A configuration similar to a supercharger can be applied.
  • the heat exchange medium flowing into the inlet header sucks at least a part of the heat exchange medium that has already flowed into the inlet header, and the heat exchange medium that flows into the inlet header and has already flowed into the inlet header.
  • a mechanism for mixing and blowing out at least a part of the heat exchange medium is more preferable as the differential pressure generating mechanism.
  • An example of such a mechanism is an ejector, and when the heat exchange medium is discharged from the ejector nozzle (orifice z constricted portion) at high speed (inflow into the inlet header), the inside of the nozzle is depressurized.
  • the ejector includes a type in which the heat exchange medium in the inlet header is sucked and mixed using the pressure drop caused by blowing the heat exchange medium.
  • At least a part of the circulation line of the inlet header can be constituted by a double pipe or a porous pipe (multiple pipe, multi-flow pipe). It is preferable that a differential pressure generating mechanism is provided at one end of the double tube or multiple tube, and that the other end of the double tube or multiple tube is communicated. By doing so, at least a part of the double pipe or the multiple pipe can be used as a circulation line.
  • another aspect of the present invention provides a plurality of tubes, an inlet header for distributing the heat exchange medium to the plurality of tubes, and an outlet header for recovering the plurality of tube force heat exchange media.
  • the inlet header is a circulation pipe through which at least a part of the heat exchange medium flowing into the inlet header can circulate, and a plurality of tubes are connected to at least a part of the circulation pipe. It is a heat exchanger including pipes.
  • Another aspect of the present invention is a header for distributing a heat exchange medium to a plurality of tubes.
  • This header includes a circulation conduit that allows at least a part of the heat exchange medium flowing into the header to circulate, and a circulation conduit in which a plurality of tubes are connected to at least a part of the circulation conduit.
  • This header can be provided with a differential pressure generating mechanism driven by the inflowing heat exchange medium.
  • the differential pressure generating mechanism preferably blows the heat exchange medium in the axial direction of the circulation pipe.
  • the differential pressure generating mechanism uses the heat exchange medium flowing into the header to suck and mix at least a part of the heat exchange medium that has flowed into the header (already flowed) and blow it out to the circulation pipe. It is desirable to use a projector.
  • the present invention includes a heat exchange system including the heat exchanger of one embodiment of the present invention and an apparatus (medium supply system) for supplying a heat exchange medium to the heat exchanger.
  • heat exchange systems or systems include refrigeration or refrigeration cycles and refrigeration equipment, refrigeration equipment, air conditioning equipment, storage, showcases, etc. including such cycles.
  • Cooling cycle A system suitable as a refrigeration cycle or a refrigeration cycle uses the heat exchanger of one embodiment of the present invention as an evaporator, pressurizes a heat exchange medium recovered from the evaporator, and cools the pressurized heat exchange medium. System with a condenser.
  • the ejector also functions as expansion means for reducing the pressure of the pressurized heat exchange medium and supplying it to the evaporator. Therefore, an inlet header force circulation pipe and an ejector for sucking and mixing at least a part of the heat exchange medium flowing into the inlet header and blowing out to the circulation pipe by the heat exchange medium flowing into the inlet header, and Heat exchange that includes is suitable for cycles and Z or systems that circulate refrigerant as a heat exchange medium.
  • the medium supply system may include expansion means for depressurizing the pressurized heat exchange medium and supplying it to the evaporator, or may be omitted.
  • FIG. 1 is a diagram showing an outline of a heat exchange system including a heat exchanger.
  • FIG. 2 is a diagram showing an outline of a heat exchanger that works on the first embodiment.
  • FIG. 3 is a diagram showing an outline of a heat exchanger that works on the second embodiment.
  • FIG. 4 is a diagram showing an outline of a part of a heat exchanger that works according to a third embodiment.
  • FIG. 5 is a diagram showing an outline of a part of a heat exchanger that works according to a fourth embodiment.
  • FIG. 6 is a diagram showing an outline of a heat exchanger that works on the fifth embodiment.
  • FIG. 7 is a diagram showing an example provided with different types of ejectors.
  • FIG. 8 is a diagram showing an outline of a heat exchanger that works on a sixth embodiment.
  • FIG. 9 is a diagram showing a cross section of the header.
  • FIG. 10 An expanded view of the header structure.
  • FIG. 1 shows a system 50 that includes heat exchangers.
  • This system (heat exchange system) 50 includes an air conditioner and a refrigeration apparatus, and includes other systems that have a heat exchange cycle and a heat exchange cycle called a cooling cycle or a refrigeration cycle.
  • the system 50 is an air conditioning system
  • the system (heat exchange system) 50 includes a liquid (liquid) heat exchange medium (hereinafter referred to as a refrigerant) R and an external fluid (for example, outdoor air) F. Exchange heat with.
  • a refrigerant liquid (liquid) heat exchange medium
  • F external fluid
  • System 50 uses heat exchange with refrigerant R It has an evaporator (evaporator) 100 that cools indoor air G, and a condenser (condenser) 200 that exchanges heat between the compressed gaseous refrigerant R and the external fluid F to make the refrigerant R liquid.
  • evaporator evaporator
  • condenser condenser
  • system 50 includes compressor 51 that pressurizes refrigerant R in addition to capacitor 200, and refrigerant R temporarily. It includes an accumulator 52 that stores energy and an expansion valve 53 that expands the refrigerant R supplied to the evaporator 100.
  • the refrigerant R force in the evaporator 100 also flows out the refrigerant outlet force of the evaporator 100, passes through the accumulator 52, the compressor 51, the condenser 200, and the expansion valve 53, and the refrigerant-filled loca of the evaporator 100 again It circulates so as to flow into the evaporator 100.
  • FIG. 2 shows a heat exchange 100 & which is useful for the first embodiment of the present invention.
  • This heat exchange 100 a can be used as the evaporator 100 of the system 50.
  • the heat exchanger 100 a includes an inlet header 1 including a refrigerant inlet 6, an outlet header 2 including a refrigerant outlet 5, and a heat exchange unit 20.
  • the inlet header 1 and the outlet header 2 extend in the vertical direction, and are arranged in parallel to each other.
  • the heat exchanging unit 20 is for exchanging heat between the refrigerant R and the air G to cool the air G and the like.
  • the heat exchanging unit 20 includes a plurality of tubes 4 arranged in parallel to each other in a horizontal direction so that the inlet header 1 and the outlet header 2 communicate with each other, and fins 3 extending in the vertical direction perpendicular to the tubes 4. It is equipped with.
  • a typical tube 4 may be a flat tube having a circular cross section, and a perforated tube (multiple tube) in which the inside of the tube is divided into a plurality of portions. It's okay.
  • a typical example of the fin 3 is a plurality of plate-like fins arranged parallel to each other and attached so that the tube 4 passes therethrough.
  • the fin 3 may be a corrugated fin that connects between the tubes 4 while meandering, or a fin or a pin protruding from the tube 4.
  • the inlet header 1 has a function as a distributor for distributing the refrigerant R to the plurality of tubes 4 of the heat exchange unit 20.
  • the outlet header 2 has a function of collecting the refrigerant R from each tube 4.
  • Each tube 4 is connected to the inlet header 1 at one end. Connected to the outlet header 2 at the other end.
  • multiple tubes 4 can increase the heat exchange area by the tube itself, and by providing fin 3, the heat exchange area (contact area) with air G etc. can be further increased. Heat exchange efficiency. In order to avoid the effects of icing, frosting, etc., fins may not be provided, and the area occupied by fins may be reduced.
  • the inlet header 1 includes a circulation line 10 and a differential pressure generating mechanism 11 for forcibly circulating at least a part of the refrigerant R flowing into the inlet header 1.
  • the circulation conduit 10 includes a straight tubular forward passage 10a and a substantially U-shaped return passage 10b in which one end force of the forward passage 10a is also connected to the other end.
  • the forward path 10a guides the refrigerant R from the refrigerant inlet 6 at one end to the opposite end.
  • the return path 10b conversely, guides the refrigerant from the opposite end of the forward path 10a to the refrigerant inlet 6. Therefore, at least a part of the refrigerant R flowing into the inlet header 1 can be circulated by the circulation line 10 including the forward path 10a and the return path 10b.
  • the differential pressure generating mechanism 11 is an ejector that includes a throttle portion 7 and a suction portion 8, and is provided in the vicinity of the refrigerant inlet 6 of the inlet header 1.
  • the return path 10b of the circulation line 10 connects the vicinity of the back end (upper end) 15 opposite to the refrigerant inlet 6 of the inlet header 1 and the suction part 8 of the differential pressure generating mechanism 11 Is provided. Therefore, the differential pressure generating mechanism 11 is driven by the refrigerant R flowing into the inlet header 1, and sucks and mixes at least a part of the refrigerant (existing refrigerant) R that has already flowed into the inlet header 1 through the return path 10b. , Blow out to outbound 10a.
  • a plurality of tubes 4 are connected to an outward path 10a which is a part of the circulation line 10. That is, a plurality of tubes 4 are connected at substantially equal intervals between the suction path 9 that is a branch of the return path 10b of the circulation pipe 10 and the differential pressure generating mechanism 11.
  • the refrigerant R in a two-phase state, in which gas and liquid are mixed, is generated by the action of the accumulator 52, compressor 51, expansion valve 53, etc.
  • the refrigerant is supplied from the refrigerant inlet 6 to the inlet header 1 and passes through the throttle portion 7 of the suction portion 8.
  • the pressure inside the throttle portion 7 is reduced. By this pressure reduction, at least a part of the existing refrigerant R that has flowed into the inlet header 1 through the suction portion 8 via the return path 10b is sucked.
  • the cold flowing into the inlet header 1 The medium R and at least a part of the refrigerant R flowing into the inlet header 1 are mixed, and as indicated by arrows in FIG. 2, the refrigerant R flows from the differential pressure generating mechanism 11 to the inside of the inlet header 1 to the circulation pipe. It is ejected in the direction of the axis L of the road 10. And a part of it returns to the suction part 8 through the forward path 10a and the return path 10b again. For this reason, at least a part of the refrigerant R is forcibly circulated in the header 1, so that the state of the refrigerant R in the pipe-like inlet header 1 having a long shaft length is uniform. Become. In other words, by giving a pressure difference in which the refrigerant R is forced to circulate in the header 1, it is possible to prevent the occurrence of a state where the liquid phase and the gas phase are separated due to the head difference in a static state. .
  • a plurality of tubes 4 are connected at substantially equal intervals in the middle of the forward path 10a through which the refrigerant R flows from the bottom to the top. Part of the refrigerant R from the inlet header 1 is distributed to each tube 4, and the state of the refrigerant R distributed to each tube 4 can be made uniform. Further, since the state of the refrigerant R in the forward path 10a is homogenized including the state of gas-liquid mixing, the amount of the refrigerant R distributed to each tube 4 can be made uniform.
  • Five forces are also drained into the system 50. Therefore, the heat exchange load in each tube 4 is made uniform.
  • a heat exchanger can be provided at a relatively low cost. Further, since the shape of each tube 4 can be made the same, the occurrence of a pressure loss difference in each tube 4 can be prevented, and in this respect, the heat exchange efficiency can be improved.
  • the heat exchanger 100a it is possible to prevent the phase separation at the inlet header 1 due to the head difference. For this reason, the arrangement direction (direction) of the inlet header 1 of the heat exchanger 100a can be freely set. Accordingly, the heat exchanger 100a may be used in a posture in which the inlet header 1 is arranged in the horizontal direction, or may be used in a posture in which the inlet header 1 is arranged in the vertical direction. Further, when the inlet header 1 is used in the vertical direction, the refrigerant R is added to the inlet. The refrigerant R that can flow from the lower side of the inlet 1 may flow into the upper force of the inlet header 1. Furthermore, unlike these postures, heat exchange 100 & can be used in various postures, including the placement of the inlet header 1 at an angle, and multiple heat exchanges 100 & Refrigerant R can be evenly distributed to tube 4.
  • the cooling system 50 including the heat exchanger 100a can be arranged in a compact manner. Furthermore, this heat exchange ⁇ 100a employs a differential pressure generation mechanism 11 that uses the ejector effect, so that in addition to the power source generally used for heat exchange ⁇ Does not require a new power source. Therefore, it is economical. Also, by assigning a part of the pressure loss due to the expansion valve 53 to the ejector 11, which is a differential pressure generating mechanism, the heat exchange efficiency can be improved without impairing the economic efficiency of the system 50. If the expansion (pressure loss) by the ejector 11 is sufficient, the expansion valve 53 can be omitted.
  • FIG. 3 shows a heat exchanger 100b that is useful for the second embodiment of the present invention.
  • This heat exchange lOOb can also be used as the evaporator 100 of the heat exchange system 50 as described above.
  • a plurality of tubes 4 are connected to the return path 10b of the circulation line 10 of the inlet header 1 at almost equal intervals.
  • the state of the refrigerant R is almost constant not only in the forward path 10a but also in the return path 10b. Therefore, even if each tube 4 is connected to the return path 10b, the refrigerant R can be distributed almost uniformly to each tube 4.
  • the position at which the ejector 11 is located slightly away from the throttle portion 7 than the position immediately after the throttle portion 7, for example, the return path 10 b, is cooled by suction mixing. Since each tube 4 is connected to the return path 10b, the ejector 11 having the throttle portion 7 and each tube 4 are separated from each other. Therefore, the refrigerant R having a stable phase state can be distributed to each tube 4.
  • Fig. 4 shows a heat exchanger 100c that is useful for the third embodiment of the present invention.
  • This heat exchange lOOc can also be used as the evaporator 100 of the heat exchange system 50 as described above.
  • the inlet header 1 includes a U-shaped pipe including two straight pipe portions, and the U-shaped open side is connected by a suction path 9. Shi Therefore, the inlet header 1 includes a circulation pipe (circulation circuit) 10, and a plurality of tubes 4 are connected to both the forward path 10 a and the return path 10 b of the circulation pipe 10. Therefore, it is almost uniform with respect to the multiple tubes 4 arranged in two rows in the forward path 10a and the return path 10b.
  • FIG. 5 shows a heat exchanger 100d that is useful in the fourth embodiment of the present invention.
  • This heat exchanger 100d includes two heat exchange portions 20a and 20b, and can be used as the evaporator 100 of the heat exchange system 50 as described above.
  • the heat exchange sections 20a and 20b are provided with a common inlet header 1, and a plurality of tubes 4 of one heat exchange section 20a are connected to the forward path 10a of the circulation pipe 10 of the header 1.
  • the plurality of tubes 4 of the other heat exchange section 20b are connected to the return path 10b. Therefore, the refrigerant R can be evenly distributed to each of the tubes 4 of the plurality of heat exchanging portions 20a and 20b by using one inlet header 1.
  • FIG. 6 shows a heat exchanger 100e that can be applied to the fifth embodiment of the present invention.
  • This heat exchanger 100e can also be used as the evaporator 100 of the heat exchange system 50 as described above.
  • the circulation pipe 10 is configured by them.
  • the plurality of tubes 4 are connected to the outer pipe 12b that is the return path.
  • the circulation line 10 can be constructed inside of one tube may further provide a compact heat ⁇ having a simple appearance.
  • FIG. 7 shows a different example of the differential pressure generating mechanism 11.
  • the differential pressure generating mechanism 11 of each of the above embodiments is an ejector in which a suction part 8 is provided in the throttle part 7 of the bench lily tube. against these The differential pressure generating mechanism 11 shown in FIG. 7 is a spray type ejector.
  • This differential pressure generating mechanism 11 includes a suction nozzle 17 for generating a differential pressure for suction in the vicinity of the refrigerant inlet 6 of the header 1, and reduces the refrigerant R flowing into the header 1 to reduce the circulation pipe. Blow out in the axial direction of the forward path 10a.
  • a suction arch I hole 18 for sucking the existing refrigerant R already flowing into the header 1 from the return path 10b is provided. For this reason, due to the pressure drop caused by the refrigerant R blown from the suction nozzle 17, the refrigerant R flowing into the header 1 from the return path 10b is sucked into the forward path 10a and blown out in the axial direction of the forward path 10a. For this reason, the refrigerant R is forcibly circulated through the circulation line 10 constituting the header 1 by the differential pressure generating mechanism 11.
  • FIG. 8, FIG. 9, and FIG. 10 show a configuration in the vicinity of the header 1 of the heat exchanger 100f that works according to the sixth embodiment of the present invention.
  • This heat exchange ⁇ f can also be used as the evaporator 100 of the heat exchange system 50 as described above.
  • the inlet header 1 of this heat exchange ⁇ 100f is composed of a double pipe 12 having an inner pipe 12a and an outer pipe 12b.
  • the inner pipe 12a and the outer pipe 12b communicate with each other at the upper part of the header 1.
  • the outer tube 12b is composed of two members 13a and 13b having a semicircular cross section formed by extrusion and cutting.
  • a plurality of flat tubes 14 are attached to the inner member 13b, and these flat tubes 14 are connected to an outlet header (not shown).
  • a member 15 having a semicircular cross section is attached to the outer member 13a to constitute an inner tube 12a. Both ends of the two members 13a and 13b constituting the outer tube 12b are closed by the cap 16.
  • a nozzle 17 is attached to the lower end of the inner pipe 12a, and the refrigerant R flowing into the header 1 is blown out into the inner pipe 12a. This nozzle 17 becomes a differential pressure generating mechanism 11, and the outer pipe lb force is applied to the inner pipe 12a by the suction force of the refrigerant R blown out with the lower force of the inner pipe 12a directed upward. It is sucked into the inner pipe 12a through the lower gap 18.
  • the header 1 includes the inner pipe 12a and the outer pipe 12b, and has the circulation path 10 communicating with the tube 14.
  • the refrigerant R is forced to circulate through the circulation path 10. It is done. For this reason, the state of the refrigerant R inside the header 1 can be made more uniform, high heat exchange efficiency and heat exchange can be provided.
  • the header is used in a posture arranged along the vertical direction.
  • the heat exchange described above is taken as an example, but heat exchange can also be used in a posture in which the headers are arranged along the horizontal direction.
  • the differential pressure generating mechanism driven by the heat exchange medium flowing into the header and at least a part of the heat exchange medium flowing into the header are circulated.
  • the circulation means is not limited to this.
  • the circulating means may be any means that forcibly circulates at least a part of the heat exchange medium (refrigerant) flowing into the header.
  • a differential pressure generating mechanism provided with an ejector nozzle is a preferred example of the present invention, and is provided in the vicinity of the refrigerant inlet of the header, whereby the refrigerant flowing into the inlet header is used. At least a part of the refrigerant flowing into the inlet header can be sucked and mixed, and the mixed refrigerant can be blown out to the header. Therefore, it is suitable for a system including a cycle and a cycle for circulating the refrigerant as described above, in which the internal pressure of the heat exchanger is set low.
  • One of the other examples of the differential pressure generating mechanism driven by the refrigerant flowing into the header is that the turbine is rotated by the pressure of the driving unit, and the differential pressure generating part (pressurizing part) such as a coaxial compressor is used.
  • a supercharger is configured to forcibly suck in the heat exchange medium.
  • the drive portion and the differential pressure generating portion (pressurizing portion) are separated and mechanically connected.
  • a differential pressure generating mechanism such as a pump that operates with separate power.
  • the differential pressure generating mechanism may be a mechanism that sends out the refrigerant circulating in the inlet header without mixing it with the refrigerant flowing into the inlet header.
  • a differential pressure generating mechanism such as a pump pressurizes the refrigerant in the inlet header and forcibly circulates it.
  • the differential pressure generating mechanism does not have to be provided near the refrigerant inlet of the header.
  • Such a differential pressure generating mechanism may be provided in the middle of the circulation pipeline, for example, a pipeline not connected to the header in the forward route or the return route, a connection route of these pipelines, or the like. It is also possible to adopt a configuration in which the differential pressure generating mechanism can be attached to and detached from the circulation line of the header.
  • a heat exchange included in the embodiment of the present invention is provided by additionally installing a pipe line functioning as a forward path or a return path and an appropriate differential pressure generating mechanism for a header of a type in which refrigerant does not circulate.
  • ⁇ and heat exchange system can also be configured.
  • a heat exchanger having a plate-like fin as a heat exchange unit is taken as an example.
  • the shape of the fin is not limited to a plate shape.
  • the shape and configuration of the heat exchanging unit are not limited to these as long as the heat exchanging unit can exchange heat between the refrigerant (heat exchanging medium) and an external fluid such as air. It is not something.
  • the system of the present invention is not limited to air conditioning, but includes devices and systems that include various types of heat exchange as part of their functions, such as radiators, various cooling devices, and various refrigeration devices.

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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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Abstract

La présente invention concerne un échangeur de chaleur qui comporte des tuyaux (4), un collecteur d'entrée (1) pour distribuer un réfrigérant dans les tuyaux (4) et un collecteur de sortie (2) pour collecter le réfrigérant provenant des tuyaux (4). Le collecteur d'entrée (1) inclut un trajet de tuyau de circulation (10) en mesure de faire circuler au moins une partie du réfrigérant s'étant écoulé dans le collecteur d'entrée (1), et les tuyaux (4) sont connectés sur le côté de trajet vers l'avant (10a) du trajet de circulation (10). Le collecteur d'entrée (1) inclut en outre un éjecteur (11) qui aspire, mélange et expulse, par un effet du réfrigérant s'écoulant dans le collecteur d'entrée (1), une partie du réfrigérant s'étant écoulé dans le collecteur d'entrée. Le collecteur d'entrée (1) est en mesure de fournir un réfrigérant dans un état plus uniforme aux tuyaux (4) connectés au trajet de circulation (10).
PCT/JP2007/052760 2006-02-15 2007-02-15 Echangeur de chaleur WO2007094422A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP07714290A EP1985949A1 (fr) 2006-02-15 2007-02-15 Echangeur de chaleur
JP2008500546A JP4866416B2 (ja) 2006-02-15 2007-02-15 熱交換器
US12/279,620 US20100314090A1 (en) 2006-02-15 2007-02-15 Heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-037791 2006-02-15
JP2006037791 2006-02-15

Publications (1)

Publication Number Publication Date
WO2007094422A1 true WO2007094422A1 (fr) 2007-08-23

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PCT/JP2007/052760 WO2007094422A1 (fr) 2006-02-15 2007-02-15 Echangeur de chaleur

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US (1) US20100314090A1 (fr)
EP (1) EP1985949A1 (fr)
JP (1) JP4866416B2 (fr)
CN (1) CN101384868A (fr)
WO (1) WO2007094422A1 (fr)

Cited By (15)

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CN110567196A (zh) * 2019-09-10 2019-12-13 江苏科菱库精工科技有限公司 一种微通道换热器的制冷剂分配装置及使用方法
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JP2012042121A (ja) * 2010-08-19 2012-03-01 Hitachi Appliances Inc 冷媒分配器及び冷凍サイクル装置
JP2013002775A (ja) * 2011-06-20 2013-01-07 Sharp Corp パラレルフロー型熱交換器及びそれを搭載した空気調和機
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WO2015045564A1 (fr) * 2013-09-30 2015-04-02 ダイキン工業株式会社 Échangeur thermique et climatiseur
JP2015068623A (ja) * 2013-09-30 2015-04-13 ダイキン工業株式会社 熱交換器および空気調和装置
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CN105849498A (zh) * 2013-12-27 2016-08-10 大金工业株式会社 热交换器及空调装置
WO2015098860A1 (fr) * 2013-12-27 2015-07-02 ダイキン工業株式会社 Échangeur thermique et dispositif de climatisation
EP3088833A4 (fr) * 2013-12-27 2017-02-01 Daikin Industries, Ltd. Échangeur de chaleur et dispositif de climatisation
EP3088832A4 (fr) * 2013-12-27 2017-02-01 Daikin Industries, Ltd. Échangeur thermique et dispositif de climatisation
WO2016017460A1 (fr) * 2014-07-31 2016-02-04 三菱電機株式会社 Distributeur de fluide frigorigène, échangeur de chaleur, et appareil à cycle de réfrigération
JPWO2016017460A1 (ja) * 2014-07-31 2017-04-27 三菱電機株式会社 冷媒分配器、熱交換器および冷凍サイクル装置
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WO2016052299A1 (fr) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Échangeur thermique et appareil de climatisation
CN106716045A (zh) * 2014-09-30 2017-05-24 大金工业株式会社 热交换器和空调装置
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JP5850118B1 (ja) * 2014-09-30 2016-02-03 ダイキン工業株式会社 熱交換器および空気調和装置
JP2016125748A (ja) * 2014-12-26 2016-07-11 ダイキン工業株式会社 熱交換器および空気調和装置
JP2016148480A (ja) * 2015-02-12 2016-08-18 株式会社デンソー 熱交換器
WO2018061359A1 (fr) * 2016-09-28 2018-04-05 東芝キヤリア株式会社 Échangeur de chaleur et dispositif à cycle frigorifique
WO2020089966A1 (fr) * 2018-10-29 2020-05-07 三菱電機株式会社 Échangeur de chaleur et dispositif à cycle de réfrigération
JPWO2020089966A1 (ja) * 2018-10-29 2021-09-02 三菱電機株式会社 熱交換器及び冷凍サイクル装置
JP2022043207A (ja) * 2018-10-29 2022-03-15 三菱電機株式会社 熱交換器、室外機、及び冷凍サイクル装置
JP7086264B2 (ja) 2018-10-29 2022-06-17 三菱電機株式会社 熱交換器、室外機、及び冷凍サイクル装置
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US20100314090A1 (en) 2010-12-16

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