CN101384868A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN101384868A CN101384868A CNA2007800051798A CN200780005179A CN101384868A CN 101384868 A CN101384868 A CN 101384868A CN A2007800051798 A CNA2007800051798 A CN A2007800051798A CN 200780005179 A CN200780005179 A CN 200780005179A CN 101384868 A CN101384868 A CN 101384868A
- Authority
- CN
- China
- Prior art keywords
- heat exchange
- exchange media
- circulation line
- heat exchanger
- inlet header
- 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.)
- Pending
Links
Images
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
Landscapes
- 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
A heat exchanger (100a) includes a plurality of tubes (4), an entrance header (1) for distributing a refrigerant to the tubes (4), and an exit header (2) for collecting the refrigerant from the tubes (4). The entrance header (1) includes a circulating conduit (10) capable of circulating at least part of the refrigerant that has flowed into the entrance header (1), and the plurality of tubes (4) are fluidly connected to the outward channel (10a) of the circulating conduit (10). The entrance header (1) also includes an ejector 11 that uses the refrigerant flowing into the entrance header to draw and mix at least part of the refrigerant that has flowed into the entrance header and spray out the mixed refrigerant. The entrance header (1) can supply refrigerant more uniformly to the tubes (4) connected to the circulating conduit (10).
Description
Technical field
The present invention relates to be used for the heat exchanger of freezing or cooling device etc.
Background technology
In heat exchanger, in order to improve heat exchanger effectiveness, the many pipes that the heat exchange media uniform distribution of supplying with collector is used to heat exchange are important.But at heat exchanger, particularly in evaporimeter (vaporizer) etc., the general heat exchange media (refrigerant) that flows into is the two-phase state that comprises gas phase and liquid phase.For this reason, be separated in the inside of collector than great and be subject to gravity to influence liquid component and proportion little and feel bad the gas componant of gravity effect, cause the refrigerant maldistribution of the many pipes of using to heat exchange easily.The inhomogeneities of the distribution of such heat exchange media is particularly remarkable under the situation of the posture use heat exchanger that becomes vertical direction with collector.For this reason, seek a kind of heat exchange media of refrigerant etc. that makes to the more uniform heat exchanger of the distribution of pipe.
As everyone knows, in order to improve inhomogeneous that refrigerant distributes, as heat exchanger, open communique 2004-317056 number the product that many distributing pipes is bent to separately three-dimensional distributor by different shapes that is equipped with of Japan Patent as the prior art introduction.In addition, in the document, disclose many distributing pipes have been concentrated on the heat exchanger that the part of the inlet header that liquid coolant retains is configured.
In the disclosed heat exchanger that distributor is housed of the document, many distributing pipes must be different separately shapes and bend to three-dimensional complicated shape.Therefore, the quantity of parts is many, and its manufacturing cost increases easily.And then, owing to for the distributing pipe that disposes the three-dimensional bending shape needs the space, so collector and heat exchanger maximize easily.
And then the described heat exchanger of the document has the refrigerant distributor gear that has used flat distributing pipe, the part of collector, particularly concentrates flat distributing pipe in collector lower part that liquid refrigerants retains easily, makes liquid refrigerants flow into heat exchange department.Under the situation of such structure, the refrigerant state of the inlet of many flat distributing pipes is near evenly, but it is poor to produce the pressure loss of the pipe that the length difference by pipe causes, and must be uniform so not talkative refrigerant to many pipes distributes.And then, owing to form the structure that configuration has many flat distributing pipes of bend, so be difficult to provide the heat exchanger of simple structure.
Disclose a kind of evaporimeter in open communique 2000-249428 number of Japan Patent, it is equipped with: inlet header, outlet header, at the fin that crawls that extends between two collectors between many pipes that are provided with and the pipe that is folded in each adjacency.In this evaporimeter, be provided with a plurality of coolant injection devices at inlet towards inlet header.A plurality of coolant injection devices have the injection throttle orifice separately.Even be provided with the injection throttle orifice at the inlet towards collector as the described evaporimeter of the document, whole in collector refrigerant is sprayed evenly distributedly also is difficult, and then, emitted dose and distribute and be subjected to the influence of flow easily.Be difficult to by adjusting throttle orifice configuration, towards so be the overhang etc. of the pipe in collector, the structure of suitably distributing according to flow is contained on the collector.And then what, the change towards the condition of the interior pressure of, pipe etc. of collector for flow also are difficult to obtain suitable refrigerant and distribute.
Summary of the invention
A kind of mode of the present invention is to have many pipes, be used for heat exchanger that these pipes are distributed the inlet header of heat exchange medias and are used for reclaiming from these pipes the outlet header of heat exchange medias.The inlet header of this heat exchanger comprises: circulation line, and it is at least a portion circulation line capable of circulation that flows into the heat exchange media of this inlet header, many pipes are connected at least a portion of this circulation line; Produce the mechanism (differential pressure generating mechanism) of differential pressure, it is used for the direction of principal axis of heat exchange media to circulation line blown out, and makes at least a portion of the heat exchange media that flows into inlet header follow endless tube road forced circulation.
According to this heat exchanger, the at least a portion that flows into (having flowed into) heat exchange media (existing heat exchange media in the inlet header) of inlet header is blown out to the direction of principal axis of circulation line by differential pressure generating mechanism, manages circulation forcibly in the circulation line that is communicated with many.Therefore, can make the state of heat exchange media of the inside of the circulation line that constitutes inlet header become more even or near state uniformly.For example, even under the situation that the heat exchange media of the two-phase state that comprises gas phase and liquid phase flows into, also can suppress heat exchange media and in inlet header, be separated into liquid phase ingredient and gas phase composition.Therefore, axial length is long to a certain degree inlet header, even connect many pipes under the state that the direction of principal axis along this inlet header disperses, also can distribute heat exchange media to each Guan Yigeng uniform state.
According to this heat exchanger, can save the distributing pipe that needs three-dimensional bending.In addition, also can save the bending machining that is used to make the uniform distribution heat exchange media and carries out to the pipe side.This does not get rid of the situation that this heat exchanger comprises the pipe arrangement of these three-dimensional pipe arrangements, bending machining.But, utilize this heat exchanger, can make the phase state of the heat exchange media of distributing to each pipe and flow forms evenly or more near its state with simpler structure.Therefore, can provide heat exchanger effectiveness good heat exchanger less expensively.
One example of differential pressure generating mechanism is that the external impetus with pump etc. drives.In cooling system etc., there is the heat exchange media of inflow heat exchanger to reduce pressure in advance or expands.If be applicable to the heat exchanger of such system, can use the energy drives differential pressure generating mechanism of heat exchange media.In this case, owing to generally do not need to be used for the power source new power source in addition of heat exchanger, so be economical.That is, wish that differential pressure generating mechanism drives by the heat exchange media that flows into inlet header.As differential pressure generating mechanism, for example can use the pressure that utilizes drive part that turbine is rotated, the booster that sucks heat exchange media forcibly by the differential pressure generating part (pressures partially) of coaxial compressor etc. is the structure of (being similar to booster) like that.
Be used for having flow at least a portion of the heat exchange media of inlet header, at least a portion mixing that makes heat exchange media that flow into inlet header and the heat exchange media that has flow into inlet header and the mechanism that blows out by the heat exchange media attraction that flows into inlet header, mechanism is even more ideal as differential pressure generating.An example of mechanism is an injector like this, from injector nozzle (throttle orifice/restriction) when at a high speed spraying heat exchange media (inflow inlet header), the nozzle interior decompression.By this decompression, the at least a portion that flows into the heat exchange media (existing heat exchange media) of inlet header is attracted, flowing into the heat exchange media of inlet header and at least a portion of the heat exchange media that flows into inlet header mixes, by circulation line, at least a portion that flows into the heat exchange media of inlet header circulates forcibly.In addition, comprising also in injector that utilization descends by the pressure that blows out heat exchange media from nozzle and produce attracts in the heat exchange media of inlet header and the type of mixing.
Its at least a portion of the circulation line of inlet header is made of dual pipe or antipriming pipe (multiple pipe, many flow channel tubes).An end that is preferably in dual pipe or multiple pipe is provided with differential pressure generating mechanism, and the other end of this dual pipe or multiple pipe constitutes in the mode that is communicated with.By such work, can be at least a portion of dual pipe or multiple pipe as circulation line.
Can separate supply to differential pressure generating mechanism from inlet header and/or heat exchanger.Thereby, another aspect of the present invention, be to have many pipes, be used for heat exchanger that these pipes are distributed the inlet header of heat exchange medias and are used for reclaiming from these pipes the outlet header of heat exchange medias, this inlet header comprises: circulation line, it is that at least a portion circulation line, the many pipes capable of circulation that flow into the heat exchange media of this inlet header are connected at least a portion of this circulation line.In addition, another aspect of the present invention is the collector that is used for heat exchange media is distributed to many pipes.The circulation line that at least a portion of the heat exchange media that flow into this collector of possessing this collector can circulate is equipped with at least a portion of this circulation line and connects many pipes.The differential pressure generating mechanism that is driven by the heat exchange media that flows into can be set on this collector.Differential pressure generating mechanism preferably blows out heat exchange media from this differential pressure generating mechanism to the direction of principal axis of circulation line.In addition, differential pressure generating mechanism is injector preferably, and at least a portion that its heat exchange media that is used for flowing into this collector attracts to mix the heat exchange media that flow into this collector (flowing into) blows out to circulation line.
And then, the present invention includes the heat-exchange system that heat exchanger with mode of the present invention and heat exchanger are supplied with the device (medium feed system) of heat exchange media.Such heat-exchange system or system comprise: cool cycles or freeze cycle and comprise such circulation refrigerating plant, cooling device, aircondition, deposit storehouse, showcase etc.As cool cycles or the optimal system of freeze cycle the heat exchanger of a mode of the present invention as evaporimeter, have the device of the heat exchange media pressurization of reclaiming and the condenser of the heat exchange media after the cooling pressurization from this evaporimeter.
Injector is also as making the heat exchange media decompression after the pressurization and supplying with the expansion mechanism performance function of evaporimeter.Therefore, the inlet header of described heat exchanger comprises circulation line and is used for attract mixing at least a portion of the heat exchange media that has flow into inlet header and the injector that blows out to circulation line by the heat exchange media that flow into inlet header, and described heat exchanger is suitable for circulation and/or system that refrigerant is circulated as heat exchange media.The system that comprises this heat exchanger can comprise the expansion mechanism that makes the heat exchange media decompression of pressurizeing and supply with evaporation yg device in the medium feed system, also can omit.
Description of drawings
Fig. 1 is the skeleton diagram that expression comprises the heat-exchange system of heat exchanger.
Fig. 2 is the skeleton diagram of the heat exchanger of expression first embodiment.
Fig. 3 is the skeleton diagram of the heat exchanger of expression second embodiment.
Fig. 4 is the skeleton diagram of a part of the heat exchanger of expression the 3rd embodiment.
Fig. 5 is the skeleton diagram of a part of the heat exchanger of expression the 4th embodiment.
Fig. 6 is the skeleton diagram of the heat exchanger of expression the 5th embodiment.
Fig. 7 is the illustration that the different injector of type is equipped with in expression.
Fig. 8 is the skeleton diagram of the heat exchanger of expression the 6th embodiment.
Fig. 9 is the figure of expression collector section.
Figure 10 is the figure that expression launches manifold construction.
The specific embodiment
Fig. 1 represents to comprise the system 50 of heat exchanger.This system (heat-exchange system) 50 comprises aircondition or refrigerating plant, comprises the heat exchange circulation that is called as cool cycles or freeze cycle and the system of heat exchange circulation as in addition system.For example, system 50 is as air-conditioning system the time, and this system (heat-exchange system) 50 carries out the heat exchange of heat exchange media (hereinafter referred to as the refrigerant) R and external fluid (for example outdoor air) F of liquid state (liquid).System 50 have by with the heat exchange cooling chamber of refrigerant R in the vaporizer (evaporimeter) 100 of air G make refrigerant R become liquid condenser (condensed device) 200 with gasiform refrigerant R that has been compressed and the heat exchange of external fluid F.
In addition, as making refrigerant R circulate, supply with the medium feed system 55 of refrigerant R to vaporizer 100, system 50 also has the liquid reservoir 52 that to the compressor 51 of refrigerant R pressurization, temporarily stores refrigerant R, the equipment such as expansion valve 53 that make the refrigerant R expansion of supplying with vaporizer 100 except that condenser 200.In this system 50, refrigerant R in the vaporizer 100 flows out from the refrigerant exit of this vaporizer 100, circulate by liquid reservoir 52, compressor 51, condenser 200, expansion valve 53, so that flow into once more in this vaporizer 100 from the refrigerant inlet of vaporizer 100.
Fig. 2 represents the heat exchanger 100a of first embodiment of the present invention.The vaporizer 100 that this heat exchanger 100a can be used as system 50 uses.This heat exchanger 100a has inlet header 1, the outlet header 2 that comprises refrigerant exit 5 and the heat exchange department 20 that comprises refrigerant inlet 6.Inlet header 1 and outlet header 2 extend respectively along the vertical direction, are configured to parallel to each other.Heat exchange department 20 is the equipment that is used for carrying out heat exchange, cooling air G etc. between refrigerant R and air G etc.Heat exchange department 20 have so that the mode that inlet header 1 and outlet header 2 is communicated with is parallel to each other in the horizontal direction configuration many pipes 4 and with the fin 3 that extends along the vertical direction of pipe 4 quadratures.
Differential pressure generating mechanism 11 is injectors that restriction 7 and attraction portion 8 are housed, be located at inlet header 1 refrigerant inlet 6 near.The road 10b that returns of circulation line 10 is arranged to connecting together with near the enter the mouth attraction portion 8 with differential pressure generating mechanism 11 of end (upper end) 15 of inboard of 6 opposition sides of refrigerant inlet header 1.Thereby differential pressure generating mechanism 11 is driven by the refrigerant R that flows into inlet header 1, by returning at least a portion that road 10b attracts to mix refrigerant (existing refrigerant) R that has flowed into inlet header 1, yearns for road 10a and blows out.In the inlet header 1 of this heat exchanger 100a, many pipes 4 be connected as the part of circulation line 10 on the 10a of road.That is, between the attraction path 9 of the branch that returns road 10b that becomes circulation line 10 and differential pressure generating mechanism 11 by roughly uniformly-spaced connecting many pipes 4.
In the heat exchanger 100a that the evaporimeter as heat-exchange system 50 is suitable for, because the effect of liquid reservoir 52, compressor 51, expansion valve 53 etc., the refrigerant R of the two-phase state that gas and liquid mix supplies with inlet header 1 from refrigerant inlet 6, by the restriction 7 of attraction portion 8.When refrigerant R flowed in the inlet header 1 via restriction 7 with high speed, the inside of restriction 7 was depressurized.By this decompression, attract to flow at least a portion of the existing refrigerant R of inlet headers 1 by returning the road 10b attraction portion 8 that flows through.Then, the refrigerant R that flows into the refrigerant R of inlet header 1 and flow at least a portion of inlet header 1 mixes, and shown in the arrow among Fig. 2, the refrigerant R direction that 1 inside follows the axle L on endless tube road 10 from differential pressure generating mechanism 11 to inlet header sprays.Then, its part is once more by toward road 10a and return road 10b and return attraction portion 8.Therefore, at least a portion of refrigerant R is forced to circulation in the inside of collector 1, and thus, even the inlet header 1 of the elongated tubular of axial length, the state of the refrigerant R of portion is also even within it.That is,, can prevent under static state to form the state that produces the liquid and gas separation by head difference in advance by offering the pressure differential that in collector 1, makes refrigerant R forced circulation.
Thereby, in this heat exchanger 100a, refrigerant R by below flow upward in the way of road 10a, manage 4 roughly uniformly-spaced to connect many.By the part that inlet header 1 distributes refrigerant R to each pipe 4, the state that can make the refrigerant R of the pipe 4 that is assigned to each is evenly.In addition, also comprise the state of gas-liquid mixed and homogenized, so realize being assigned to the homogenising of the amount of respectively managing 4 refrigerant R at the state of the refrigerant R on the 10a of road.
Like this, be evenly distributed to and respectively manage 4 refrigerant R and carry out heat exchange,, in the system of system 50, flow out from refrigerant exit 5 to outlet header 2 outputs by many pipes 4, multi-disc fin 3 and air G etc.Thereby, make and respectively manage 4 heat exchange duty homogenising, obtain the good heat exchanger 100a of heat exchanger effectiveness.And then, needn't can provide the less expensive good heat exchanger of heat exchanger effectiveness with simple compact structure for to each pipe uniform distribution refrigerant and with many distributing pipe bidimensionals or three-dimensional bend to different separately shapes.In addition, make identically owing to can manage 4 shape to each, so can prevent the generation of the pressure loss difference in each pipe 4, this point also can improve heat exchanger effectiveness.
In addition, according to this heat exchanger 100a, in inlet header 1, can prevent by being separated that head difference causes.Therefore, can freely set the inlet header 1 of heat exchanger 100a the configuration direction (towards).Thereby heat exchanger 100a promptly can use with the posture that inlet header 1 along continuous straight runs is disposed, also can be so that inlet header 1 is used along the posture of vertical direction configuration.And then, under the situation that inlet header 1 is used along the vertical direction configuration, both can make the following side inflow of refrigerant R from inlet header 1, refrigerant R is flowed into from the top of inlet header 1.And then, can make the various postures of inlet header 1 tilted configuration use heat exchanger 100a by comprise different with these postures, when using heat exchanger 100a by these postures, can be to many pipe 4 uniform distribution refrigerant R.
And then, because the miniaturization of heat exchanger 100a is easy, so the cooling system 50 of this heat exchanger 100a can compact Layout be housed.And then, because this heat exchanger 100a adopts and to have used the differential pressure generating mechanism 11 of jet effect, so do not need generally to be used for the power source of heat exchanger, the new power source except that the power of compressor 51 for example.From but economical.And, by the part of the crushing that is produced by expansion valve 53 being distributed to injector 11, can make the not loss of economy of system 50 as differential pressure generating mechanism, realize improving heat exchanger effectiveness.In addition, if the expansion (pressure loss) that is produced by injector 11 is enough, also can omit expansion valve 53.
Fig. 3 represents the heat exchanger 100b of second embodiment of the present invention.The vaporizer 100 that this heat exchanger 100b also can be used as heat-exchange system 50 as described above uses.In this heat exchanger 100b, many pipes 4 returning on the 10b of road by the circulation line 10 that is connected inlet header 1 about equally at interval.In the circulation line 10 of the refrigerant R forced circulation that makes at least a portion, be not limited to toward road 10a, in returning road 10b, the state of refrigerant R is roughly necessarily.Thereby, be connected and return on the 10b of road even respectively manage 4, also can manage 4 uniform distribution refrigerant R roughly at each.In addition, leave the position of restriction 7 a little and for example return the position, dead astern that 10b one side in road compares the restriction 7 of injector 11, attract the phase state of the refrigerant R of mixing to stablize more easily.In this heat exchanger 100b, because each pipe 4 is connected and returns on the 10b of road, so separate between the injector 11 with restriction 7 and each pipe 4.Thereby, can manage 4 at each and distribute mutually in stable condition refrigerant R.
Fig. 4 represents the heat exchanger 100c of the 3rd embodiment of the present invention.The vaporizer 100 that this heat exchanger 100c also can be used as above-mentioned heat-exchange system 50 uses.In this heat exchanger 100c, inlet header 1 comprises the pipe of the U font that contains 2 straight sections, and then the open sides of this U font is by attracting path 9 to connect.Thereby inlet header 1 comprises circulation line (closed circuit) 10, this circulation line 10 toward road 10a and return all connect on road 10b two sides many pipe 4.Thereby, can to toward road 10a and many of two-column parallel pipes 4 returning road 10b with substantially uniformly state supply with refrigerant R.According to this heat exchanger 100c, can not change the area (projected area) on the plane of heat exchange department 20, further improve the rate of heat exchange in the heat exchange department 20.
Fig. 5 represents the heat exchanger 100d of the 4th embodiment of the present invention.This heat exchanger 100d has two heat exchange department 20a and 20b, and the vaporizer 100 that can be used as above-mentioned heat-exchange system 50 uses.In this heat exchanger 100d, heat exchange department 20a and 20b have common inlet header 1, and the many pipes 4 that connect a heat exchange department 20a on the 10a of road at the circulation line 10 of this collector 1 are returning many pipes 4 that connect another heat exchange department 20b on the 10b of road.Thereby, can distribute refrigerant R to inlet header of pipe 4 usefulness 1 equalization of a plurality of heat exchange department 20a and 20b respectively.The heat exchange department that can connect on an inlet header also can be more than three.
Fig. 6 represents the heat exchanger 100e of the 5th embodiment of the present invention.The vaporizer 100 that this heat exchanger 100e also can be used as above-mentioned heat-exchange system 50 uses.The inlet header 1 of this heat exchanger 100e comprises dual pipe 12, and differential pressure generating mechanism (injector) 11 is located at the bottom of dual pipe 12.In addition, the interior pipe 12a and the outer tube 12b of the upper end of dual pipe 12 are interconnected.In this inlet header 1, setting can blow out the injector 11 of refrigerant R along the direction of principal axis of the interior pipe 12a of dual pipe 12 inboards.Thereby the interior pipe 12a of dual pipe 12 constitutes toward the road, and outer tube 12b forms and returns the road, constitutes circulation line 10 thus.And many pipes 4 are connected as returning on the outer tube 12b on road.At this heat exchanger 100a, owing to can constitute circulation line 10 in the inside of one pipe, and then the heat exchanger with compact simple outward appearance can be provided.Realize circulation line 10 for pipe, be not limited to dual pipe, also can use the multiple pipe (antipriming pipe) that the right quantity next door is housed in inside with one.
Fig. 7 represents the different example of differential pressure generating mechanism 11.The differential pressure generating mechanism 11 of each above-mentioned embodiment is the injector that attraction portion 8 is set in the restriction 7 of Venturi tube.Relative therewith, differential pressure generating mechanism 11 shown in Figure 7 is injectors of aerosol type.This differential pressure generating mechanism 11 has the attraction nozzle 17 that is used to produce the differential pressure that attracts usefulness near the refrigerant of collector 1 inlet 6, make the refrigerant R decompression that flows into collector 1, blows out to the direction of principal axis of the past road 10a of circulation line.Be used for from returning the attraction hole 18 that road 10b attracts to have flowed into the existing refrigerant R of collector 1 toward being provided with near the attraction nozzle 17 of road 10a.Therefore, descend by the pressure that produces from the refrigerant R that attracts nozzle 17 to blow out, from returning road 10b, the refrigerant R that flows into collector 1 is inhaled into toward road 10a, and the direction of principal axis of yearning for road 10a blows out.Therefore, refrigerant R is forced to circulation by differential pressure generating mechanism 11 in the circulation line 10 that constitutes collector 1.
Fig. 8, Fig. 9 and Figure 10 represent near the structure the collector 1 of heat exchanger 100f of the 6th embodiment of the present invention.The vaporizer 100 that this heat exchanger 100f also can be used as above-mentioned heat-exchange system 50 uses.The inlet header 1 of this heat exchanger 100f is made of the dual pipe 12 of pipe 12a and outer tube 12b in having, and interior pipe 12a and outer tube 12b are communicated with on the top of collector 1.Further specifically, outer tube 12b is that semicircular two parts 13a and 13b form by the section that forms by extruding and cutting.Many flat tubes 14 are installed on the parts 13b of inboard, these flat tubes 14 with do not have illustrated outlet header to connect together.It is pipe 12a in semicircular parts 15 constitute that section is installed on the parts 13a in the outside.Constituting two the parts 13a of outer tube 12b and the two ends of 13b is clogged by lid 16.Nozzle 17 is installed on the lower end of interior pipe 12a, and the inside of inwardly managing 12a blows out the refrigerant R that flows into collector 1.This nozzle 17 becomes differential pressure generating mechanism 11, by the attraction of the refrigerant R that upwards blows out under interior pipe 12a, via the gap 18 of the downside of interior pipe 12a, inwardly manages 12a from outer tube 1b and attracts existing (having flowed into) refrigerant R.
In this heat exchanger 100f, pipe 12a and outer tube 12b in collector 1 comprises have and pipe 14 circulating paths that are communicated with 10, and refrigerant R is circulated in circulating path 10 forcibly.Therefore, the state of the refrigerant R of collector 1 inside can be more even, can provide heat exchanger effectiveness high heat exchanger.
In above-mentioned first to the 6th embodiment, the heat exchanger that uses along the posture of vertical direction configuration with collector is illustrated as example, but heat exchanger also can dispose the attitude use of collector by along continuous straight runs.
In addition, has cycling mechanism in above-mentioned first to the 6th the embodiment, it possesses the differential pressure generating mechanism that is driven by the heat exchange media that flows into collector and is used to make the circulation line of at least one circulation of the heat exchange media that flows into collector, but cycling mechanism is not limited to this.Cycling mechanism so long as make the heat exchange media (refrigerant) that flows into collector at least one forced circulation mechanism just.
Differential pressure generating mechanism with injector nozzle (throttle orifice, restriction), as suitable example of the present invention, near the refrigerant inlet that is located at collector, can attract to mix at least a portion of the refrigerant that has flow to inlet header with the refrigerant that flows into to inlet header, blow out the refrigerant of admixture to collector.Thereby, be suitable for setting lowly to the interior pressure of heat exchanger, comprise circulation that makes above-mentioned refrigerant circulation and the system that comprises circulation.
Another example of the differential pressure generating mechanism that drives with the refrigerant that flows into collector is that the pressure with drive part rotates turbine, with the such structure of booster of differential pressure generating part (pressures partially) pressure suction heat exchange media of coaxial compressor etc.The structure approximate with this booster, the structure that has drive part mechanically to be connected with differential pressure generating part (pressures partially) separation.And then, also can adopt the differential pressure generating mechanism that utilizes other power-actuated pump such.That is, differential pressure generating mechanism does not mix the mechanism that just sends to the refrigerant that circulates with the refrigerant that flow into inlet header in inlet header.The such differential pressure generating mechanism of pump is the mechanism of the refrigerant in the inlet header being pressurizeed, carrying out forced circulation, and differential pressure generating mechanism also can not be located near the refrigerant inlet of collector.Such differential pressure generating mechanism also can be located in the way of circulation line, for example toward the road or return on the pipeline that does not connect collector in the road, the access path of these pipelines etc.In addition, also can adopt the structure of the circulation line mounting or dismounting differential pressure generating mechanism of collector relatively.
And then relative refrigerant is the collector of circular form not, by appending as past road or returning the pipeline of road performance function and suitable differential pressure generating mechanism, also can constitute heat exchanger and heat-exchange system that embodiments of the present invention comprise.
In the present embodiment, the heat exchanger that has tabular fin with heat exchange department is that example is illustrated, but that the shape of fin is not limited to is tabular.In addition, heat exchange department is so long as can carry out heat exchange just between the external fluid of refrigerant (heat exchange media) and air etc., and the shape and the structure of heat exchange department also are not limited thereto.
In addition, system of the present invention is not limited to air-conditioning, also comprises comprising device, the system of diversified heat exchanges such as radiator, various cooling device, various refrigerating plants as the part of function.
Claims (12)
1. heat exchanger, this heat exchanger has:
Many pipes,
Be used for to described many pipes distribute heat exchange medias inlet header and
Be used for reclaiming the outlet header of heat exchange media from described many pipes;
Described inlet header comprises:
Circulation line, this circulation line are to have flow into the circulation line that at least a portion of the heat exchange media in this inlet header can circulate, described many pipes be connected at least a portion of this circulation line and
Differential pressure generating mechanism, this differential pressure generating mechanism blows out the direction of principal axis of heat exchange media to described circulation line, makes at least a portion forced circulation in described circulation line that flow into the described heat exchange media in the described inlet header.
2. heat exchanger as claimed in claim 1 is characterized in that, described differential pressure generating mechanism is driven by the heat exchange media that flows into described inlet header.
3. heat exchanger as claimed in claim 1, it is characterized in that described differential pressure generating mechanism is used for utilizing the heat exchange media that flows into described inlet header to come at least a portion to the heat exchange media that flow into described inlet header to attract the mechanism of mixing and blowing out.
4. heat exchanger as claimed in claim 1, it is characterized in that, described inlet header has the dual pipe or the multiple pipe of at least one portion that constitutes described circulation line, and described differential pressure generating mechanism is located at an end of described dual pipe or multiple pipe, and the other end of described dual pipe or multiple pipe is communicated with.
5. system, this system have heat exchanger as claimed in claim 1 and described heat exchanger are supplied with the medium feed system of heat exchange media.
6. system as claimed in claim 5 is characterized in that, the condenser that described medium feed system has device that the heat exchange media that reclaims from described heat exchanger is pressurizeed and pressurized heat exchange media is cooled off.
7. heat exchanger, this heat exchanger has:
Many pipes,
Be used for to described many pipes distribute heat exchange medias inlet header and
Be used for reclaiming the outlet header of heat exchange media from described many pipes;
Described inlet header comprises circulation line, and this circulation line is to have flow into the circulation line that at least a portion of the heat exchange media in this inlet header can circulate, and described many pipes are connected at least a portion of this circulation line.
8. heat exchanger, this heat exchanger has:
Many pipes,
Be used for to described many pipes distribute heat exchange medias inlet header and
Be used for reclaiming the outlet header of heat exchange media from described many pipes;
Described inlet header comprises:
Circulation line, this circulation line are to have flowed into the circulation line that at least a portion of the heat exchange media of this inlet header can circulate, described many pipes be connected at least a portion of this circulation line and
Injector, this injector are used to utilize the heat exchange media that flows into described inlet header that at least a portion of the heat exchange media that flows into described inlet header is attracted to mix and blow out to described circulation line.
9. heat-exchange system, this heat-exchange system have heat exchanger as claimed in claim 8 and described heat exchanger are supplied with the medium feed system of heat exchange media as evaporimeter;
Described medium feed system has the device that the heat exchange media that reclaims from described evaporimeter is pressurizeed and cools off the condenser of the heat exchange media after pressurized.
10. collector, this collector are used for many pipes are distributed heat exchange medias, it is characterized in that,
Have circulation line, this circulation line is to have flowed into the circulation line that at least a portion of the heat exchange media of this collector can circulate, and described many pipes are connected at least a portion of this circulation line.
11. collector as claimed in claim 10, it is characterized in that, further has differential pressure generating mechanism, this differential pressure generating mechanism utilizes the heat exchange media that flows into this collector, blows out the heat exchange media of at least a portion that comprises the heat exchange media that flows into this collector to the direction of principal axis of described circulation line.
12. collector as claimed in claim 10, it is characterized in that, further have injector, this injector utilization flows into the heat exchange media of this collector, and at least a portion of the heat exchange media that flows into this collector is attracted to mix and blow out to described circulation line.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP037791/2006 | 2006-02-15 | ||
| JP2006037791 | 2006-02-15 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101384868A true CN101384868A (en) | 2009-03-11 |
Family
ID=38371599
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007800051798A Pending CN101384868A (en) | 2006-02-15 | 2007-02-15 | Heat exchanger |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20100314090A1 (en) |
| EP (1) | EP1985949A1 (en) |
| JP (1) | JP4866416B2 (en) |
| CN (1) | CN101384868A (en) |
| WO (1) | WO2007094422A1 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011032346A1 (en) * | 2009-09-16 | 2011-03-24 | Ni Jun | Constant-pressure and measured-power refrigeration system for refrigeration equipment |
| CN102470729A (en) * | 2009-10-13 | 2012-05-23 | 昭和电工株式会社 | Intermediate heat exchanger |
| CN103206885A (en) * | 2013-03-27 | 2013-07-17 | 广东美的电器股份有限公司 | Header pipe, parallel flow heat exchanger and air conditioner |
| CN105518411A (en) * | 2013-09-11 | 2016-04-20 | 大金工业株式会社 | Heat exchanger and air conditioner |
| CN105593628A (en) * | 2013-09-30 | 2016-05-18 | 大金工业株式会社 | Heat exchanger and air conditioner |
| CN105849498A (en) * | 2013-12-27 | 2016-08-10 | 大金工业株式会社 | Heat exchanger and air conditioning device |
| CN107208944A (en) * | 2015-02-02 | 2017-09-26 | 株式会社电装 | The one-piece type heat exchanger of injector |
| CN112888910A (en) * | 2018-10-29 | 2021-06-01 | 三菱电机株式会社 | Heat exchanger and refrigeration cycle device |
| CN114623702A (en) * | 2020-12-11 | 2022-06-14 | 杭州三花微通道换热器有限公司 | Heat exchanger |
| TWI809718B (en) * | 2021-02-26 | 2023-07-21 | 日商三菱電機股份有限公司 | Heat exchanger and refrigeration cycle apparatus |
Families Citing this family (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009150574A (en) * | 2007-12-19 | 2009-07-09 | Mitsubishi Electric Corp | Distributor, and heat exchanger and air conditioner loading the same |
| JP5567935B2 (en) * | 2010-08-19 | 2014-08-06 | 日立アプライアンス株式会社 | Refrigerant distributor and refrigeration cycle apparatus |
| JP5763436B2 (en) * | 2011-06-20 | 2015-08-12 | シャープ株式会社 | Parallel flow type heat exchanger and air conditioner equipped with the same |
| CN103148729B (en) * | 2013-03-19 | 2015-01-21 | 丹佛斯微通道换热器（嘉兴）有限公司 | Collecting main and heat exchanger with same |
| US9670937B2 (en) * | 2013-05-30 | 2017-06-06 | Ingersoll-Rand Company | Centrifugal compressor having cooling system |
| CN105431704B (en) | 2013-08-12 | 2018-07-27 | 开利公司 | Heat exchanger and flow distributor |
| JP6179399B2 (en) * | 2013-12-27 | 2017-08-16 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
| JP5741680B1 (en) * | 2013-12-27 | 2015-07-01 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
| JP6188951B2 (en) * | 2014-07-31 | 2017-08-30 | 三菱電機株式会社 | Refrigerant distributor, heat exchanger and refrigeration cycle apparatus |
| US10197312B2 (en) * | 2014-08-26 | 2019-02-05 | Mahle International Gmbh | Heat exchanger with reduced length distributor tube |
| JP5850118B1 (en) * | 2014-09-30 | 2016-02-03 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
| JP6070685B2 (en) * | 2014-12-26 | 2017-02-01 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
| JP2016148480A (en) * | 2015-02-12 | 2016-08-18 | 株式会社デンソー | Heat exchanger |
| JP6425830B2 (en) * | 2015-10-26 | 2018-11-21 | 三菱電機株式会社 | Refrigerant distributor and air conditioner using the same |
| JP2019207033A (en) * | 2016-09-28 | 2019-12-05 | 東芝キヤリア株式会社 | Heat exchanger and refrigeration cycle device |
| JP6369648B1 (en) * | 2017-03-27 | 2018-08-08 | ダイキン工業株式会社 | Heat exchanger and air conditioner |
| EP3605002B1 (en) | 2017-03-27 | 2020-12-23 | Daikin Industries, Ltd. | Heat exchanger and air-conditioning device |
| CN110476035A (en) * | 2017-03-29 | 2019-11-19 | 大金工业株式会社 | Heat exchanger |
| FR3081985B1 (en) * | 2018-05-31 | 2020-10-09 | Valeo Systemes Thermiques | FLUID DISTRIBUTOR, AND CORRESPONDING THERMAL EXCHANGER. |
| JP7086264B2 (en) * | 2018-10-29 | 2022-06-17 | 三菱電機株式会社 | Heat exchanger, outdoor unit, and refrigeration cycle device |
| CN110567196A (en) * | 2019-09-10 | 2019-12-13 | 江苏科菱库精工科技有限公司 | Refrigerant distribution device of micro-channel heat exchanger and use method |
| EP3855059B1 (en) * | 2020-01-24 | 2023-11-15 | Aptiv Technologies Limited | Passive flow divider and liquid cooling system comprising the same |
Family Cites Families (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2097602A (en) * | 1936-03-06 | 1937-11-02 | Warren Webster & Co | Radiator |
| US2088609A (en) * | 1936-07-28 | 1937-08-03 | Randel Bo Folke | Method of and apparatus for refrigerating |
| US2766740A (en) * | 1955-03-07 | 1956-10-16 | Adolph A Tacchella | Cooling system for internal combustion engines |
| US2825317A (en) * | 1956-01-09 | 1958-03-04 | Adolph A Tacchella | Steam separator |
| DE3413931A1 (en) * | 1984-04-13 | 1985-10-24 | Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co. KG, 7000 Stuttgart | EVAPORATOR, ESPECIALLY FOR AIR CONDITIONING IN MOTOR VEHICLES |
| JPH06127695A (en) * | 1991-07-15 | 1994-05-10 | Kanebo Ltd | Cup cutout device |
| JPH0790251B2 (en) * | 1991-09-25 | 1995-10-04 | 川崎製鉄株式会社 | Spray header and rolling oil supply device using the same |
| JP3265649B2 (en) * | 1992-10-22 | 2002-03-11 | 株式会社デンソー | Refrigeration cycle |
| JPH0910817A (en) * | 1995-06-27 | 1997-01-14 | Kawasaki Steel Corp | Spray header for rolling oil lubricant and its use |
| US5910167A (en) | 1997-10-20 | 1999-06-08 | Modine Manufacturing Co. | Inlet for an evaporator |
| JPH11337293A (en) * | 1998-05-26 | 1999-12-10 | Showa Alum Corp | Evaporator |
| US6688137B1 (en) * | 2002-10-23 | 2004-02-10 | Carrier Corporation | Plate heat exchanger with a two-phase flow distributor |
| JP2004232924A (en) * | 2003-01-29 | 2004-08-19 | Denso Corp | Refrigeration cycle device |
| JP3818270B2 (en) * | 2003-04-17 | 2006-09-06 | 株式会社デンソー | Heat exchanger |
| JP4259478B2 (en) * | 2004-02-18 | 2009-04-30 | 株式会社デンソー | Evaporator structure and ejector cycle |
| US20050262872A1 (en) * | 2004-05-26 | 2005-12-01 | Carrier Corporation | Two-phase refrigerant distribution system for parallel tube evaporator coils |
| US7331195B2 (en) * | 2004-10-01 | 2008-02-19 | Advanced Heat Transfer Llc | Refrigerant distribution device and method |
-
2007
- 2007-02-15 US US12/279,620 patent/US20100314090A1/en not_active Abandoned
- 2007-02-15 JP JP2008500546A patent/JP4866416B2/en active Active
- 2007-02-15 WO PCT/JP2007/052760 patent/WO2007094422A1/en active Search and Examination
- 2007-02-15 EP EP07714290A patent/EP1985949A1/en not_active Withdrawn
- 2007-02-15 CN CNA2007800051798A patent/CN101384868A/en active Pending
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2011032346A1 (en) * | 2009-09-16 | 2011-03-24 | Ni Jun | Constant-pressure and measured-power refrigeration system for refrigeration equipment |
| CN102470729A (en) * | 2009-10-13 | 2012-05-23 | 昭和电工株式会社 | Intermediate heat exchanger |
| CN103206885A (en) * | 2013-03-27 | 2013-07-17 | 广东美的电器股份有限公司 | Header pipe, parallel flow heat exchanger and air conditioner |
| CN105518411A (en) * | 2013-09-11 | 2016-04-20 | 大金工业株式会社 | Heat exchanger and air conditioner |
| CN105593628B (en) * | 2013-09-30 | 2018-07-03 | 大金工业株式会社 | Heat exchanger and air-conditioning device |
| CN105593628A (en) * | 2013-09-30 | 2016-05-18 | 大金工业株式会社 | Heat exchanger and air conditioner |
| CN105849498A (en) * | 2013-12-27 | 2016-08-10 | 大金工业株式会社 | Heat exchanger and air conditioning device |
| CN107208944A (en) * | 2015-02-02 | 2017-09-26 | 株式会社电装 | The one-piece type heat exchanger of injector |
| CN107208944B (en) * | 2015-02-02 | 2019-08-13 | 株式会社电装 | The one-piece type heat exchanger of injector |
| CN112888910A (en) * | 2018-10-29 | 2021-06-01 | 三菱电机株式会社 | Heat exchanger and refrigeration cycle device |
| CN112888910B (en) * | 2018-10-29 | 2022-06-24 | 三菱电机株式会社 | Heat exchanger and refrigeration cycle device |
| CN114623702A (en) * | 2020-12-11 | 2022-06-14 | 杭州三花微通道换热器有限公司 | Heat exchanger |
| CN114623702B (en) * | 2020-12-11 | 2023-08-29 | 杭州三花微通道换热器有限公司 | Heat Exchanger |
| TWI809718B (en) * | 2021-02-26 | 2023-07-21 | 日商三菱電機股份有限公司 | Heat exchanger and refrigeration cycle apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2007094422A1 (en) | 2007-08-23 |
| JPWO2007094422A1 (en) | 2009-07-09 |
| JP4866416B2 (en) | 2012-02-01 |
| EP1985949A1 (en) | 2008-10-29 |
| US20100314090A1 (en) | 2010-12-16 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101384868A (en) | Heat exchanger | |
| CN100476319C (en) | Refrigerant distribution device and method | |
| CN100575813C (en) | Multi-part heat exchanger | |
| CN101622504B (en) | Unit for ejector type refrigeration cycle and refrigeration device using the same | |
| JP2009041876A (en) | Heat exchanger | |
| CN110822757A (en) | Carbon dioxide refrigerating system and refrigerating method thereof | |
| US20080190134A1 (en) | Refrigerant flow distributor | |
| CN103822406A (en) | Heat pump heat exchanger having low pressure drop distribution pipe | |
| CN102564215A (en) | Heat exchanger washing device and air conditioner having the same | |
| CN102032825A (en) | Heat exchange tube for evaporator and evaporator formed by same | |
| CN112833589B (en) | Condenser and air conditioner comprising same | |
| CN203758089U (en) | Micro-channel heat exchanger and air conditioner with micro-channel heat exchanger | |
| CN101149203B (en) | Cooling device and assembling body | |
| CN105823254A (en) | Ejector and heat pump apparatus | |
| CN208490108U (en) | A kind of refrigeration system suitable for container-type data center | |
| CN105299966B (en) | Micro-channel heat exchanger and air-conditioning | |
| CN102735077A (en) | Efficient shell and tube heat exchanger with changeable inner diameter of heat exchange pipe | |
| CN110168302A (en) | For distributing the device of refrigerant in the pipe of heat exchanger for constituting refrigerant circuit | |
| CN212538117U (en) | Air conditioning unit with spray cooling system | |
| CN106989632B (en) | Finned heat exchanger system and method with auxiliary tube | |
| CN212777709U (en) | Air conditioning unit with spray cooling system | |
| CN212538118U (en) | Air conditioning unit with spray cooling system | |
| CN205279532U (en) | Microchannel heat exchanger and air conditioner | |
| CN1102225C (en) | Air conditioner heat-exchanger | |
| CN209672656U (en) | A kind of falling film evaporator and its novel distributor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |