CN101419002A - Parallel flow heat exchanger and use - Google Patents

Parallel flow heat exchanger and use Download PDF

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Publication number
CN101419002A
CN101419002A CNA2008100425167A CN200810042516A CN101419002A CN 101419002 A CN101419002 A CN 101419002A CN A2008100425167 A CNA2008100425167 A CN A2008100425167A CN 200810042516 A CN200810042516 A CN 200810042516A CN 101419002 A CN101419002 A CN 101419002A
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parallel flow
header
flow heat
current drainage
crosspoint
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CN101419002B (en
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王磊
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Wang Lei
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Abstract

The invention relates to a parallel flow heat exchanger, which comprises at least two stacked parallel flow heat exchange units, wherein each parallel flow heat exchange unit comprises a top flow collecting pipe, a bottom flow collecting pipe, and a plurality of parallel flat pipes communicating the top flow collecting pipe and the bottom flow collecting pipe; and the axial flowing length of a heat exchange medium on the top flow collecting pipe is larger than that on the bottom flow collecting pipe; and the axial flowing length on the top flow collecting pipe is as long as possible, while the axial flowing length on the bottom flow collecting pipe is as short as possible. The parallel flow heat exchanger improves the heat exchange medium of two-phase flow of gas and liquid remarkably, in particular solves problem of delamination of the gas and the liquid in refrigerant, so as to effectively solve the problem of uneven distribution of the gas and the liquid, improve heat exchange efficiency of the heat exchanger, and fully evaporate the refrigerant. At the same time, the parallel flow heat exchanger saves volume and reduces cost.

Description

A kind of parallel flow heat exchanger and purposes
Technical field
The present invention relates to the heat exchanger channels design field, relate in particular to a kind of parallel flow heat exchanger and purposes that adopts the gas/liquid two phase flow in the multilayer concurrent flow structure.
Background technology
The heat exchanger that is applied to evaporimeter and condenser at present generally is divided into stacked heat exchanger and parallel flow heat exchanger.So-called stacked heat exchanger is made up of a plurality of stacked heat exchanger units, in theory can be unrestrictedly stacked.But the heat exchanger unit of a size of the stacked heat exchanger of this class needs one group of mould to make, and approximately needs more than 100 ten thousand RMB and open such one group of mould.If the size of heat exchanger unit has changed, then need to offer the mould manufacturing separately, cause investment to increase.
So-called parallel flow heat exchanger is to be combined by flat tube and last lower header, and flat tube and last lower header adopt the cold-extrusion technology extrusion modling, all can be the section bar of standard.When making the parallel flow heat exchanger of different size, only need be according to the size of heat exchanger, the flat tube and the last lower header Combination Welding that cut appropriate length get final product, do not need to make in addition corresponding mould, therefore saved the cycle of mould manufacturing expense and product development, be widely used in the air conditioning for automobiles at present.
Be that stacked heat exchanger or parallel flow heat exchanger all relate to the gas/liquid two phase flow, fluid assignment problem how in heat exchanger.
When two phase flow is flowed through a plurality of runner that all is connected to shared entrance and exit collector, gas and liquid are because different momentum and the change of flow direction in heat exchanger, so have with the flow through trend of different runners of different flow rates, this has caused the uneven flow distribution for gas and liquid, and this directly influences heat transfer property again, particularly in the zone near the exit, the liquid quality ratio is very low usually.Dried district or hot-zone that any liquid distributes the uneven gas-liquid separation that causes will cause no liquid in various degree; Region of fluid or runner can not make all liq evaporation in addition, and then a part of liquid will flow out from this heat exchanger, and this has and adverse influence the system that uses heat exchanger.For example, in refrigerant evaporator systems, the liquid that flows out from evaporimeter causes flow control valve or expansion valve to be closed to reduce refrigerant mass flow, and this will reduce the total heat transfer of this evaporimeter, reduce exchange capability of heat.
At the conventional structure that is used for evaporimeter and condenser, two phase flow enters inlet header along common direction perpendicular to main heat transfer runner.Because gas has low-down momentum and density, so for gas, change the direction and the forward most of runners of flowing through easily, but liquid is because its bigger momentum and be higher than the density of gas hundreds of times so liquid has the trend that keeps advancing to collector bottom and end, and its result is that the minority runner after leaning on has usually than higher liquid flow rate of forward runner and lower specific gas flow rate.
In order to address the above problem, the industry had been attempted the feasible flow distribution of carrying out equably of several different methods in the past in stacked heat exchanger.A kind of method has wherein been used a kind of porose inlet header as shown in United States Patent (USP) NO.3976128.Another kind of mode is that evaporimeter is divided into a plurality of districts or is divided into the little grouping of the runner that is connected in series to together, for example United States Patent (USP) NO.4274482.Help although these methods are through-flow, the still undesirable and inefficient hot-zone of flow distribution still exists.
Also there is the technology forerunner to begin in the inlet of parallel flow heat exchanger and/or outlet header, to use block piece or separator, so that heat exchanger is divided into a plurality of sections, as shown in Figure 1, the parallel flow heat exchanger heat exchanger that U.S. Modine and Korea S person who quote make, it is by being provided with the passage that a block piece 3 forms symmetry in inlet header 1 and outlet header 2.Exactly throttle 4 is housed in the passage of symmetry in addition, parallel flow heat exchanger as shown in Figure 2 with fluid process portion's section in proper order of predetermined ratio, makes that this fluid stream in order portion section keeps in parallel and distribution more equably.
Although above-mentioned change can partly realize fluid equally distributed problem in stacked heat exchanger and parallel flow heat exchanger, its effect still is not very desirable.
The inventor finds in the parallel flow heat exchanger research process, cold-producing medium is in the header of the bottom of parallel flow heat exchanger during along bottom header axial flow, gas and liquid since the layering that the difference of kinetic energy and density causes than serious many of cold-producing medium layering during along bottom header axial flow in the header of heat exchanger top, and after gas and the liquid layering, to more seriously cause the uneven distribution of gas and liquid, this is the problem that the industry is had a headache all the time very much.
Being exactly that existing parallel flow heat exchanger adopts the segmented runner to carry out heat exchange in addition, because each section channel volume is basic identical, also is to cause the uneven major issue of flow distribution.
In addition, existing parallel flow heat exchanger all is to adopt the side to import and export, and has increased the volume of parallel flow heat exchanger like this, causes difficulty is installed.
Summary of the invention
One of technical problem to be solved by this invention is to provide a kind of parallel flow heat exchanger, to solve the existing in prior technology problems.
One of technical problem to be solved by this invention is to provide the application of above-mentioned parallel flow heat exchanger.
Parallel flow heat exchanger as first aspect present invention, the parallel flow heat crosspoint that comprises stack more than at least two, wherein each parallel flow heat crosspoint comprises top header, bottom header that constitutes whole parallel flow heat exchanger runner and the some flat tubes that are arranged in parallel that are communicated with top header and bottom header; Directly be not communicated with between the top header of described adjacent two parallel flow heat crosspoints, and part directly is communicated with mutually between the bottom header of adjacent two parallel flow heat crosspoints; It is characterized in that, described heat exchange medium at described top header along the length of top header axial flow greater than in the length of bottom header along bottom header axial flow, and long as much as possible at described top header along the length of top header axial flow, and at the length only possible weak point of bottom header along bottom header axial flow.
In the present invention, the axial flow of heat exchange medium is all finished in the header of top in the heat exchanger; Heat exchange medium flows and is then all finished through the butt joint of the hole of intercommunication by the bottom header between the parallel flow heat crosspoint of stack; The parallel flow heat exchanger runner then adopts the interior barrier plate of header in the heat exchange unit of stack runner to be divided into a plurality of sections.
According to gas-liquid two-phase flow work characteristics in the heat exchange medium, for cooperating the runner design of concurrent flow, in the present invention, the control heat exchange medium described top header along the length of top header axial flow account for heat exchange medium described top header along the length of top header axial flow with at length sum 70% or more of bottom header along bottom header axial flow, and heat exchange medium the bottom header along the length of bottom header axial flow account for heat exchange medium described top header along the length of top header axial flow with at length sum 30% below of bottom header along bottom header axial flow.
The runner of described heat exchanger is divided into a plurality of sections, and along the heat exchange medium flow direction, the channel volume of each section progressively increases, but the channel volume of last section must not be greater than 2.5 times of the channel volume of first section.Preferred version is: the volume of a back section runner is greater than last section channel volume 20-60%.More preferably scheme is: the volume of a back section runner is greater than last section channel volume 40-50%.
In the present invention, described last two sections runners are provided with the supply mouth of supplemental heat exchange media in these last two sections runners, this supply mouth can design with different shapes, quantity and seat, as long as its former velocity of medium of the not substantive destruction of medium amount that its control replenishes; Wherein the additional heat exchange medium of last runner can be the 15-20% of total heat exchange medium weight.
In the present invention, the import of described heat exchange medium and outlet are arranged on the side pipe wall of top header of a parallel flow heat crosspoint.
As the application of the parallel flow heat exchanger of second aspect present invention, this parallel flow heat exchanger runner can be used for making evaporimeter, especially is used for making the automobile parallel-flow evaporator.Can also be used to making heat pump type air-conditioner heat exchanger.As heat pump type air conditioner evaporimeter and condenser.The present invention can make full use of described heat exchanger characteristics and high efficient heat exchanging advantage structurally, medium import at heat exchanger is adopted parallel many interface structures form with exporting to design, as large scale heat exchanger runner design and distribution solution. this solution make parallel flow heat exchanger when substituting traditional copper tube aluminum formula heat exchanger, both can avoid the runner unstability that adopts the employed multithread of pipe sheet type structure road structure on evaporimeter, to bring, but the gas-liquid separation and the flow resistance size of runner design control heat exchanger medium again.
The present invention is arranged on header top and bottom and realizes making condenser in the heat pump type air-conditioner heat exchanger when parallel flow condenser is vertically installed.
Owing to adopted design as above, the present invention has improved the heat exchange medium of gas and liquid two phase flow significantly, especially gas and liquid lamination problem in the cold-producing medium, thereby solved the uneven assignment problem of gas and liquid effectively, improved the heat exchanger effectiveness of heat exchanger, cold-producing medium can be evaporated fully.Also save simultaneously the volume of heat exchanger, reduced cost.
Description of drawings
Fig. 1 is the heat converter structure principle schematic that U.S. Modine and Korea S person who quote make.
Fig. 2 is for existing Japanese by the structural principle schematic diagram of adorning designed heat exchanger.
Fig. 3 is the parallel flow heat exchanger structural principle schematic diagram of the embodiment of the invention 1.
Fig. 4 is the parallel flow heat exchanger structural principle schematic diagram of the embodiment of the invention 2.
Fig. 5 is the parallel flow heat exchanger structural principle schematic diagram of the embodiment of the invention 3.
Fig. 6 is the parallel flow heat exchanger structural principle schematic diagram of the embodiment of the invention 4.
Fig. 7 is the parallel flow heat exchanger structural principle schematic diagram of the embodiment of the invention 5.
3 layers of parallel-flow evaporator performance test curve map that Fig. 8 makes for the present invention.
W220 * H240 * T38 that Fig. 9 makes for the present invention, 4 channel parallel flow evaporator device performance test curve maps.
W242 * H255 * T38 that Figure 10 makes for the present invention, 6 channel parallel flow evaporator device performance test curve maps.
The specific embodiment
In order to make technological means of the present invention, creation characteristic, to reach purpose and effect is easy to understand,, further set forth the present invention below in conjunction with embodiment.
Embodiment 1:
Parallel flow heat exchanger as shown in Figure 3 is the evaporimeter that an automobile uses.Comprise two parallel flow heat exchanger unit that are superimposed, be convenient to describe, it is defined as the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200.
The first parallel flow heat crosspoint 100 comprises top header 110, bottom header 120 and the some flat tubes that are arranged in parallel 130 that are communicated with top header 110 and bottom header 120, the shape of flat tube 130 is with the Chinese invention patent " a kind of aluminium-made extrusion slender section " of the applicant in application on April 21st, 2006, its application number is 200610025898.3, notification number is CN1967135, is not described in detail at this.
The second parallel flow heat crosspoint 200 comprises top header 210, bottom header 220 and the some flat tubes that are arranged in parallel 230 that are communicated with top header 210 and bottom header 220, the shape of flat tube 130 is with the Chinese invention patent " a kind of aluminium-made extrusion slender section " of the applicant in application on April 21st, 2006, its application number is 200610025898.3, notification number is CN1967135, is not described in detail at this.Flat tube 230 can be to be connected as a single entity the description in 200610025898.3 inventions as application number with 130, forms double flat tube.
Directly be not communicated with between the top header 110 and 210 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, and part directly is communicated with mutually between the bottom header 120 and 220 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, and the top header 210 of the top header 110 of such first parallel flow heat crosspoint 100, bottom header 120 and flat tube 130 and the second parallel flow heat crosspoint 200, bottom header 220 and flat tube 230 constitute the whole heat exchange runner of this embodiment.The import 300 of the heat exchange medium of whole heat exchange runner and outlet 400 are arranged on the side pipe wall of top header 110 of the first parallel flow heat crosspoint 100.
In the top header 110 of the first parallel flow heat crosspoint 100 and bottom header 120, respectively be provided with a barrier plate 111 and 121, wherein barrier plate 111 and 121 is divided into N1 current drainage road and N2+N3 current drainage road with the runner in the first parallel flow heat crosspoint 100, be provided with a barrier plate 221 in the bottom header 220 of the second parallel flow heat crosspoint 200, barrier plate 221 is divided into N1+N2 current drainage road and N3 current drainage road with the second parallel flow heat crosspoint 200.N1 current drainage road in the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200 by the first parallel flow heat crosspoint 100 bottom header 120 and the opening 122 between the bottom header 220 of two parallel flow heat crosspoints 200 link up, the N3 current drainage road in the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200 by the first parallel flow heat crosspoint 100 bottom header 120 and the opening 123 between the bottom header 220 of the second parallel flow heat crosspoint 200 link up.The flow direction of cold-producing medium in whole runner is: entered by import 300 in the N1 current drainage road of top header 110 of the first parallel flow heat crosspoint 100, flat tube 130 along the N1 current drainage road of the first parallel flow heat crosspoint 100 flows to the bottom header 120 of the first parallel flow heat crosspoint 100 downwards, laterally flow in the bottom header 220 of the second parallel flow heat crosspoint 200 by opening 122 again, flat tube 230 along the N1+N2 current drainage road of the second parallel flow heat crosspoint 200 rises in the top header 210 of the second parallel flow heat crosspoint 200, again along the axial flow of top header 210, flow to the N3 current drainage road of the second parallel flow heat crosspoint 200, flat tube 230 along the N3 current drainage road of the second parallel flow heat crosspoint 200 drops in the bottom header 220 of the second parallel flow heat crosspoint 200 again, then laterally flow in the N2+N3 current drainage road of the first parallel flow heat crosspoint 100 by opening 123, flat tube 130 along the N2+N3 current drainage road of the first parallel flow heat crosspoint 100 rises in the top header 110 of the first parallel flow heat crosspoint 100, is flowed out by outlet 400.Whole cold-producing medium at flow process through four runners, i.e. N1 current drainage road, N1+N2 current drainage road, N3 current drainage road, N2+N3 current drainage road.Cold-producing medium progressively increases at the volume of four runners of flow process, the volume that is each runner is: N1 current drainage road<N1+N2 current drainage road<N3 current drainage road<N2+N3 current drainage road, the volume in N1+N2 current drainage road is greater than the 40-50% of N1 current drainage road volume, the volume in N3 current drainage road is greater than the 40-50% of N1+N2 current drainage road volume, the volume in N2+N3 current drainage road is greater than the 40-50% of N3 current drainage road volume, and the volume in N2+N3 current drainage road is 2.5 times of N1 current drainage road volume.
As can be seen from Figure 3, cold-producing medium has only N1+N2 at the bottom header 220 of the second parallel flow heat crosspoint 200 at most along the length of bottom header 220 axial flow, and be N2+N3 along the length of top header 210 axial flow at the top header 210 of the second parallel flow heat crosspoint 200, because the length of N3 is greater than N1, thus cold-producing medium at the top header 210 of the second parallel flow heat crosspoint 200 along the length of top header 210 axial flow greater than the bottom header 220 of the second parallel flow heat crosspoint 200 length along bottom header 220 axial flow.When being provided with, can make cold-producing medium long as much as possible along the length of top header 210 axial flow at the top header 210 of the second parallel flow heat crosspoint 200, account for cold-producing medium top header 110 and 210 along the length of top header 110 and 210 axial flow with at bottom header 120 and 220 along 70% of the length sum of bottom header 120 and 220 axial flow, and at the bottom header 220 of the second parallel flow heat crosspoint 200 the only possible weak point of length along bottom header 220 axial flow, account for cold-producing medium top header 110 and 210 along the length of top header 110 and 210 axial flow with at bottom header 120 and 220 along 30% of the length sum of bottom header 120 and 220 axial flow.
Embodiment 2:
Parallel flow heat exchanger as shown in Figure 4 is the evaporimeter that an automobile uses.Comprise two parallel flow heat exchanger unit that are superimposed, be convenient to describe, it is defined as the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200.
The first parallel flow heat crosspoint 100 comprises top header 110, bottom header 120 and the some flat tubes that are arranged in parallel 130 that are communicated with top header 110 and bottom header 120, and the shape of flat tube 130 is with embodiment 1.
The second parallel flow heat crosspoint 200 comprises top header 210, bottom header 220, mozzle 240 and the some flat tubes that are arranged in parallel 230 that are communicated with top header 210 and bottom header 220, and the shape of flat tube 130 is with embodiment 1.Flat tube 230 can be to be connected as a single entity the description in 200610025898.3 inventions as application number with 130, forms double flat tube.
Directly be not communicated with between the top header 110 and 210 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, and part directly is communicated with mutually between the bottom header 120 and 220 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, and the top header 210 of the top header 110 of such first parallel flow heat crosspoint 100, bottom header 120 and flat tube 130 and the second parallel flow heat crosspoint 200, bottom header 220 and flat tube 230 constitute the whole heat exchange runner of this embodiment.The import 300 of the heat exchange medium of whole heat exchange runner is arranged on the side wall of top header 210 of the second parallel flow heat crosspoint 200, and outlet 400 is arranged on the side wall of top header 110 of the first parallel flow heat crosspoint 100.
In the bottom header 120 of the first parallel flow heat crosspoint 100, be provided with in two barrier plates 121 and 124, two barrier plates 121 and 124 the bottom header 120 and be divided into N1 current drainage road, N2 current drainage road, N3+N4 current drainage road the first parallel flow heat crosspoint 100; In the top header 110 of the first parallel flow heat crosspoint 100, be provided with a barrier plate 111, be divided into N1+N2 current drainage road and N3+N4 current drainage road in the top header 110 of barrier plate 111 with the first parallel flow heat crosspoint 100.In the bottom header 220 of the second parallel flow heat crosspoint 200, be provided with in two barrier plates 221 and 222, two barrier plates 221 and 222 the bottom header 220 and be divided into N1 current drainage road, N2+N3 current drainage road, N4 current drainage road the second parallel flow heat crosspoint 200; In the top header 210 of the second parallel flow heat crosspoint 200, be provided with a barrier plate 211, be divided into N1 current drainage road and N2+N3+N4 current drainage road in the top header 210 of barrier plate 211 with the second parallel flow heat crosspoint 200.Mozzle is inserted in the top header 210 of the second parallel flow heat crosspoint 200, and its entrance point taps into mouth 300, and the port of export is positioned at the N1 current drainage road of the top header 210 of the second parallel flow heat crosspoint 200.
N1 current drainage road in the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200 by the first parallel flow heat crosspoint 100 bottom header 120 and the opening 122 between the bottom header 220 of two parallel flow heat crosspoints 200 link up, the N2+N3 current drainage road in the N2 current drainage road of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200 by the first parallel flow heat crosspoint 100 bottom header 120 and the opening 123 between the bottom header 220 of the second parallel flow heat crosspoint 200 link up.N4 current drainage road in the N3+N4 current drainage road of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200 by the first parallel flow heat crosspoint 100 bottom header 120 and the opening 125 between the bottom header 220 of the second parallel flow heat crosspoint 200 link up.
The flow direction of cold-producing medium in whole runner is: enter into mozzle 240 by import 300, enter into the N1 current drainage road of the top header 210 of second parallel flow heat exchanger 200 by mozzle 240, flat tube 230 along the N1 current drainage road of the second parallel flow heat crosspoint 200 flows to the bottom header 220 of the second parallel flow heat crosspoint 200 downwards, laterally flow in the N1 current drainage road of bottom header 120 of the first parallel flow heat crosspoints 100 by opening 122 again, rise in the N1 current drainage road of top header 110 of the first parallel flow heat crosspoint 100 along the flat tube 130 in the N1 current drainage road of the first parallel flow heat crosspoint 100, again along the axial flow of top header 110, flow in the N1 current drainage road of the first parallel flow heat crosspoint, 100 top headers 110, flow to N2 current drainage road from N1 current drainage road along the first parallel flow heat crosspoint, 100 top headers 110.Flow into cold-producing medium in the N2 current drainage road of the first parallel flow heat crosspoint, 100 top headers 110 and flow in the N2 current drainage road of bottom header of the first parallel flow heat crosspoint 100, laterally flow in the N2+N3 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200 by opening 123 again along the flat tube 130 in the N2 current drainage road of the first parallel flow heat crosspoint 100.The cold-producing medium that enters in the N2+N3 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200 flows upward in the N2+N3 current drainage road of top header 210 of the second parallel flow heat crosspoint 200 along the flat tube 230 in the N2+N3 current drainage road of the second parallel flow heat crosspoint 200.The cold-producing medium that enters in the N2+N3 current drainage road of top header 210 of the second parallel flow heat crosspoint 200 flows in the N4 current drainage road of top header 210 along the top header 210 of the second parallel flow heat crosspoint 200, is flow to downwards in the N4 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200 by the flat tube 230 in the N4 current drainage road of the second parallel flow heat crosspoint 200 again.The cold-producing medium that enters in the N4 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200 laterally flows in the N4 current drainage road of bottom header 120 of the first parallel flow heat crosspoints 100 through opening 125, then the flat tube 130 in the N4 current drainage road of the first parallel flow heat crosspoint 100 rises in the N3+N4 current drainage road of top header 110 of the first parallel flow heat crosspoint 100, is flowed out by outlet 400.
Whole cold-producing medium at flow process through six runners, i.e. N1 current drainage road, N1 current drainage road, N2 current drainage road, N2+N3 current drainage road, N4 current drainage road, N4+N3 current drainage road.Cold-producing medium is in flow process, the volume of next four runners progressively increases, the volume that is each runner is: N1 current drainage road<N2 current drainage road<N2+N3 current drainage road<N4 current drainage road<N4+N3 current drainage road, the volume in N2 current drainage road is greater than the 40-50% of N1 current drainage road volume, the volume in N2+N3 current drainage road is greater than the 40-50% of N2 current drainage road volume, the volume in N4 current drainage road is greater than the 40-50% of N2+N3 current drainage road volume, the volume in N4+N3 current drainage road is greater than the 40-50% of N4 current drainage road volume, and the volume in N4+N3 current drainage road is 2.5 times of N1 current drainage road volume.
As can be seen from Figure 4, cold-producing medium is at the bottom header 220 of the second parallel flow heat crosspoint 200 and almost do not have axial flowing in the bottom header 120 of the first parallel flow heat crosspoint 100, and the length along top header 210 axial flow is N4+N3+N2+N1+N2+N3+N4 in the top header 210 of the second parallel flow heat crosspoint 200, length along top header 110 axial flow in the top header 110 of the first parallel flow heat crosspoint 100 is N1+N2+N4, therefore be far longer than cold-producing medium the bottom header 220 of the second parallel flow heat crosspoint 200 and in the bottom header 120 of the first parallel flow heat crosspoint 100 length of axial flow.
When being provided with, can make cold-producing medium at the top header 210 of the second parallel flow heat crosspoint 200 along the length of top header 210 axial flow and long as much as possible along the length of top header 110 axial flow at the top header 110 of the first parallel flow heat crosspoint 100, account for cold-producing medium top header 110 and 210 along the length of top header 110 and 210 axial flow with at bottom header 120 and 220 along 70% of the length sum of bottom header 120 and 220 axial flow, and at the bottom header 220 of the second parallel flow heat crosspoint 200 along the length of bottom header 220 axial flow with at the bottom header 120 of the first parallel flow heat crosspoint 100 the only possible weak point of length along bottom header 120 axial flow, account for cold-producing medium top header 110 and 210 along the length of the header 110 at top and 210 axial flow with at bottom header 120 and 220 along the length sum of bottom header 120 and 220 axial flow below 30%.
In order to prevent superheating phenomenon, N3 current drainage road and this section of N4 current drainage road of being positioned at top header 210 at mozzle 240 are offered porose, replenish cold-producing medium by the N3 current drainage road and the N4 current drainage road of this hole in top header 210, wherein the cold-producing medium that replenishes to N4 current drainage road accounts for the 15-20% of whole cold-producing medium total amount.
Embodiment 3
Parallel flow heat exchanger as shown in Figure 5.Comprise three parallel flow heat exchanger unit that are superimposed, be convenient to describe, it is defined as the first parallel flow heat crosspoint 100, the second parallel flow heat crosspoint 200, the 3rd parallel flow heat crosspoint 500.
The first parallel flow heat crosspoint 100 comprises top header 110, bottom header 120 and the some flat tubes that are arranged in parallel 130 that are communicated with top header 110 and bottom header 120, and the shape of flat tube 130 is with embodiment 1.
The second parallel flow heat crosspoint 200 comprises top header 210, bottom header 220 and the some flat tubes that are arranged in parallel 230 that are communicated with top header 210 and bottom header 220, and the shape of flat tube 230 is with embodiment 1.
The 3rd parallel flow heat crosspoint 500 comprises top header 510, bottom header 520 and the some flat tubes that are arranged in parallel 530 that are communicated with top header 510 and bottom header 520, and the shape of flat tube 530 is with flat tube 130 and 230.
Flat tube 530,230 can be to be connected as a single entity the description in 200610025898.3 inventions as application number with 130, forms three rows of flat pipes.
Part directly is communicated with between the top header 110 and 210 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, and part directly is communicated with between the bottom header 120 and 220 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200.Directly be not communicated with between the top header 210 and 510 of the second parallel flow heat crosspoint 200 and the 3rd parallel flow heat crosspoint 500, part directly is communicated with between the bottom header 220 and 520 of the second parallel flow heat crosspoint 200 and the 3rd parallel flow heat crosspoint 500.The top header 510 of the top header 210 of the top header 110 of such first parallel flow heat crosspoint 100, bottom header 120 and flat tube 130, the second parallel flow heat crosspoint 200, bottom header 220 and flat tube 230, the 3rd parallel flow heat crosspoint 500, bottom header 520 and flat tube 530 constitute the whole heat exchange runner of this embodiment.The import 300 of the heat exchange medium of whole heat exchange runner and outlet 400 are arranged on the side pipe wall of bottom header 110 of the first parallel flow heat crosspoint 100.
In the top header 110 of the first parallel flow heat crosspoint 100 and bottom header 120, respectively be provided with a barrier plate 111 and 121, wherein barrier plate 111 and 121 is divided into N1 current drainage road and N2+N3+N4 current drainage road with the runner in the first parallel flow heat crosspoint 100, respectively be provided with a barrier plate 211 and 221 in the top header 210 of the second parallel flow heat crosspoint 200 and the bottom header 220, barrier plate 211 and 221 runners with the second parallel flow heat crosspoint 200 are divided into N1+N2 current drainage road and N3+N4 current drainage road; Be provided with a barrier plate 521 in the bottom header 520 of the 3rd parallel flow heat crosspoint 500, barrier plate 521 is divided into N1+N2+N3 current drainage road and N4 current drainage road with the runner in the bottom header 520 of the 3rd parallel flow heat crosspoint 200.
N1+N2 current drainage roads in N1 current drainage road in the top header 110 of the first parallel flow heat crosspoint 100 and the top header of the second parallel flow heat crosspoint 200 210 by the first parallel flow heat crosspoint 100 top header 110 and the opening 126 between the top header 210 of the second parallel flow heat crosspoint 200 link up; N3+N4 current drainage roads in N2+N3+N4 current drainage road in the top header 110 of the first parallel flow heat crosspoint 100 and the top header of the second parallel flow heat crosspoint 200 210 by the first parallel flow heat crosspoint 100 top header 110 and the opening 127 between the top header 210 of the second parallel flow heat crosspoint 200 link up.N1+N2+N3 current drainage roads in N1+N2 current drainage road in the bottom header 220 of the second parallel flow heat crosspoint 200 and the bottom header of the 3rd parallel flow heat crosspoint 500 520 by the second parallel flow heat crosspoint 100 bottom header 220 and the opening 223 between the bottom header 520 of the 3rd parallel flow heat crosspoint 500 link up; N4 current drainage roads in N3+N4 current drainage road in the bottom header 220 of the second parallel flow heat crosspoint 200 and the bottom header of the 3rd parallel flow heat crosspoint 500 520 by the second parallel flow heat crosspoint 100 bottom header 220 and the opening 224 between the bottom header 520 of the 3rd parallel flow heat crosspoint 500 link up.
The flow direction of cold-producing medium in whole runner is: entered by import 300 in the N1 current drainage road of bottom header 110 of the first parallel flow heat crosspoint 100, flow upward in the N1 current drainage road of top header 110 of the first parallel flow heat crosspoint 100 along the flat tube 130 in the N1 current drainage road of the first parallel flow heat crosspoint 100, laterally flow in the N1+N2 current drainage road of top header 210 of the second parallel flow heat crosspoints 200 by opening 126 again.Flow in the N1+N2 current drainage road of top header 210 of the second parallel flow heat crosspoint 200 cold-producing medium again the flat tube 230 in the N1+N2 current drainage road of the second parallel flow heat crosspoint 200 flow in the N1+N2 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200, then laterally flow in the N1+N2+N3 current drainage road of the bottom header 520 in the 3rd heat exchange units 500 by opening 223.The flat tube 530 of cold-producing medium in the N1+N2+N3 current drainage road of the 3rd heat exchange unit 500 that flows in the N1+N2+N3 current drainage road of the bottom header 520 in the 3rd heat exchange unit 500 upwards flows in the N1+N2+N3 current drainage road of the top header 510 in the 3rd heat exchange unit 500.Flow in the N4 current drainage road that axially flows to the top header 510 in the 3rd heat exchange unit 500 of the top header 510 of cold-producing medium in the 3rd heat exchange unit 500 in the N1+N2+N3 current drainage road of the top header 510 in the 3rd heat exchange unit 500, then the flat tube in the N4 current drainage road of the 3rd heat exchange unit 500 530 flows into downwards in the N4 current drainage road of bottom header 520 of the 3rd heat exchange units 500.Flow in cold-producing medium in the N4 current drainage road of bottom header 520 of the 3rd heat exchange unit 500 flows into the second parallel flow heat crosspoint 200 by opening 224 the N3+N4 current drainage road of bottom header 220, the flat tube 230 in the N3+N4 current drainage road of the second parallel flow heat crosspoint 200 upwards flow in the N3+N4 current drainage road in the top header 210 of the second parallel flow heat crosspoint 200 again.Flow in cold-producing medium in the N3+N4 current drainage road in the top header 210 of the second parallel flow heat crosspoint 200 flow into the first parallel flow heat crosspoint 100 by opening 127 the N2+N3+N4 current drainage road of top header 110.The cold-producing medium that flow in the N2+N3+N4 current drainage road of top header 110 of the first parallel flow heat crosspoint 100 flow into downwards in the N2+N3+N4 current drainage road of bottom header 120 of the first parallel flow heat crosspoint 100 along the flat tube 130 in the N2+N3+N4 current drainage road of the first parallel flow heat crosspoint 100 again, is flowed out by outlet 400.
Whole cold-producing medium at flow process through six runners, i.e. N1 current drainage road, N1+N2 current drainage road, N1+N2+N3 current drainage road, N4 current drainage road, N4+N3 current drainage road, N4+N3+N2 current drainage road.Cold-producing medium is in flow process, the volume of six runners progressively increases, the volume that is each runner is: N1 current drainage road<N1+N2 current drainage road<N1+N2+N3 current drainage road<N4 current drainage road<N4+N3 current drainage road<N4+N3+N2 current drainage road, the volume in N1+N2 current drainage road is greater than the 40-50% of N1 current drainage road volume, the volume in N1+N2+N3 current drainage road is greater than the 40-50% of N1+N2 current drainage road volume, the volume in N4 current drainage road is greater than the 40-50% of N1+N2+N3 current drainage road volume, the volume in N4+N3 current drainage road is greater than the 40-50% of N4 current drainage road volume, N4+N3+N2 current drainage road is greater than the 40-50% of N4+N3 current drainage road volume, and the volume in N4+N3+N2 current drainage road is 2.5 times of N1 current drainage road volume.
As can be seen from Figure 5, cold-producing medium only in the bottom header 520 of the 3rd parallel flow heat crosspoint 500 and top header 510 by along the 3rd parallel flow heat crosspoint 500 axial flow, in the first parallel flow heat crosspoint 100 and the second concurrent flow heat-exchange tube, 200 essentially no axial flow.Cold-producing medium is N1+N2+N3 in the length of bottom header 520 axial flow of the 3rd parallel flow heat crosspoint 500, and the length that axially flows in top header 510 is N4, since N1+N2+N3 current drainage road volume<N4 current drainage road volume, therefore, N1+N2+N3 length<N4 length.By along the 3rd parallel flow heat crosspoint 500 axial flow
When being provided with, can make cold-producing medium length along top header 510 axial flow in the top header 510 of the 3rd parallel flow heat crosspoint 500 long as much as possible, account for cold-producing medium at the length of top header 510 axial flow and more than 70% of length sum in bottom header 520 axial flow; Cold-producing medium is short as much as possible along the length of bottom header 520 axial flow at the bottom header 520 of the 3rd parallel flow heat crosspoint 500, accounts for cold-producing medium at the length of top header 510 axial flow and below 30% of length sum in bottom header 520 axial flow.
Embodiment 4
Parallel flow heat exchanger as shown in Figure 6.Comprise three parallel flow heat exchanger unit that are superimposed, be convenient to describe, it is defined as the first parallel flow heat crosspoint 100, the second parallel flow heat crosspoint 200, the 3rd parallel flow heat crosspoint 500.
The first parallel flow heat crosspoint 100 comprises top header 110, bottom header 120 and the some flat tubes that are arranged in parallel 130 that are communicated with top header 110 and bottom header 120, and the shape of flat tube 130 is with embodiment 1.
The second parallel flow heat crosspoint 200 comprises top header 210, bottom header 220 and the some flat tubes that are arranged in parallel 230 that are communicated with top header 210 and bottom header 220, and the shape of flat tube 230 is with embodiment 1.
The 3rd parallel flow heat crosspoint 500 comprises top header 510, bottom header 520 and the some flat tubes that are arranged in parallel 530 that are communicated with top header 510 and bottom header 520, and the shape of flat tube 530 is with flat tube 130 and 230.
Flat tube 530,230 can be to be connected as a single entity the description in 200610025898.3 inventions as application number with 130, forms three rows of flat pipes.
Part directly is communicated with between the top header 110 and 210 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, directly is not communicated with between the bottom header 120 and 220 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200.Directly be not communicated with between the top header 210 and 510 of the second parallel flow heat crosspoint 200 and the 3rd parallel flow heat crosspoint 500, part directly is communicated with between the bottom header 220 and 520 of the second parallel flow heat crosspoint 200 and the 3rd parallel flow heat crosspoint 500.The top header 510 of the top header 210 of the top header 110 of such first parallel flow heat crosspoint 100, bottom header 120 and flat tube 130, the second parallel flow heat crosspoint 200, bottom header 220 and flat tube 230, the 3rd parallel flow heat crosspoint 500, bottom header 520 and flat tube 530 constitute the whole heat exchange runner of this embodiment.The import 300 of the heat exchange medium of whole heat exchange runner is arranged on the end tube wall of top header 210 of the second parallel flow heat crosspoint 200, and outlet 400 is arranged on the end tube wall of top header 110 of the first parallel flow heat crosspoint 100.
Be provided with a barrier plate 111 in the top header 110 of the first parallel flow heat crosspoint 100, barrier plate 111 is divided into N1+N2 current drainage road and N3+N4 current drainage road with the runner in the top header 110 of the first parallel flow heat crosspoint 100; Respectively be provided with a barrier plate 211 and 221 in the top header 210 of the second parallel flow heat crosspoint 200 and bottom header 220, barrier plate 211 and 221 runners with the second parallel flow heat crosspoint 200 are divided into N1 current drainage road and N2+N3+N4 current drainage road; Be provided with a barrier plate 521 in the bottom header 520 of the 3rd parallel flow heat crosspoint 500, barrier plate 521 is divided into N1+N2+N3 current drainage road and N4 current drainage road with the runner in the bottom header 520 of the 3rd parallel flow heat crosspoint 200.
N2+N3+N4 current drainage roads in N3+N4 current drainage road in the top header 110 of the first parallel flow heat crosspoint 100 and the top header of the second parallel flow heat crosspoint 200 210 by the first parallel flow heat crosspoint 100 top header 110 and the opening 128 between the top header 210 of the second parallel flow heat crosspoint 200 link up; N1+N2+N3 current drainage roads in N1 current drainage road in the bottom header 210 of the second parallel flow heat crosspoint 200 and the bottom header of the 3rd parallel flow heat crosspoint 500 510 by the second parallel flow heat crosspoint 200 bottom header 210 and the opening 225 between the bottom header 510 of the 3rd parallel flow heat crosspoint 500 link up.N4 current drainage roads in N2+N3+N4 current drainage road in the bottom header 220 of the second parallel flow heat crosspoint 200 and the bottom header of the 3rd parallel flow heat crosspoint 500 520 by the second parallel flow heat crosspoint 100 bottom header 220 and the opening 226 between the bottom header 520 of the 3rd parallel flow heat crosspoint 500 link up.
The flow direction of cold-producing medium in whole runner is: entered by import 300 in the N1 current drainage road of top header 210 of the second parallel flow heat crosspoint 200, flow to downwards in the N1 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200 along the flat tube 230 in the N1 current drainage road of the second parallel flow heat crosspoint 200, laterally flow in the N1 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoints 500 by opening 225 again.Flow into cold-producing medium in the N1 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoint 500 again in the N2+N3 current drainage road of the bottom header 520 that axially flows to the 3rd parallel flow heat crosspoint 500 of the 3rd parallel flow heat crosspoint 500.Flowing to the flat tube 530 of cold-producing medium in the N2+N3 current drainage road of the 3rd parallel flow heat crosspoint 500 in the N2+N3 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoint 500 flows upward in the N2+N3 current drainage road of top header 510 of the 3rd parallel flow heat crosspoint 500.Flow in cold-producing medium in the N2+N3 current drainage road of top header 510 of the 3rd parallel flow heat crosspoint 500 axially flows to the 3rd parallel flow heat crosspoint 500 along the top header 510 of the 3rd parallel flow heat crosspoint 500 the N4 current drainage road of top header 510.Flow to the flat tube 530 of cold-producing medium in the N4 current drainage road of the 3rd parallel flow heat crosspoint 500 in the N4 current drainage road of top header 510 of the 3rd parallel flow heat crosspoint 500 and flow to downwards in the N4 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoint 500, flow in the N2+N3+N4 current drainage road in the bottom header 220 of the second parallel flow heat crosspoint 200 by opening 226 again.Flow in the N2+N3+N4 current drainage road of top header 210 that the flat tube 230 of cold-producing medium in the N2+N3+N4 current drainage road of the second parallel flow heat crosspoint 200 in the N2+N3+N4 current drainage road in the bottom header 220 of the second parallel flow heat crosspoint 200 upwards flow into the second parallel flow heat crosspoint 200.Flow in cold-producing medium in the N2+N3+N4 current drainage road of top header 210 of the second parallel flow heat crosspoint 200 laterally flow into the first parallel flow heat crosspoint 100 by opening 128 the N3+N4 current drainage road of top header 110, then the flat tube 130 in the N3+N4 current drainage road of the first parallel flow heat crosspoint 100 flow into downwards in the N3+N4 current drainage road in the bottom header 120 of the first parallel flow heat crosspoint 100.Flow into cold-producing medium in the N3+N4 current drainage road in the bottom header 120 of the first parallel flow heat crosspoint 100 along the axial flow of the bottom header 120 of the first parallel flow heat crosspoint 100 in the N1+N2 current drainage road of the bottom header 120 of the first parallel flow heat crosspoint 100, flat tube 130 in the N1+N2 current drainage road of the first parallel flow heat crosspoint 100 upwards flows in the N1+N2 current drainage road of top header 110 of the first parallel flow heat crosspoint 100 again, flows out from exporting 400.
Whole cold-producing medium at flow process through six runners, i.e. N1 current drainage road, N1+N2+N3 current drainage road, N4 current drainage road, N2+N3+N4 current drainage road, N4+N3 current drainage road, N1+N2 current drainage road.Cold-producing medium is in flow process, the volume of six runners progressively increases, the volume that is each runner is: N1 current drainage road<N1+N2+N3 current drainage road<N4 current drainage road<N2+N3+N4 current drainage road<N4+N3 current drainage road<N1+N2 current drainage road, the volume in N1+N2+N3 current drainage road is greater than the 40-50% of N1 current drainage road volume, the volume in N4 current drainage road is greater than the 40-50% of N1+N2+N3 current drainage road volume, the volume in N2+N3+N4 current drainage road is greater than the 40-50% of N4 current drainage road volume, the volume in N2+N3+N4 current drainage road is greater than the 40-50% of N4 current drainage road volume, 2 (N4+N3) current drainage road is greater than the 40-50% of N2+N3+N4 current drainage road volume, the volume in 2 (N1+N2) current drainage road is greater than the 40-50% of the volume in 2 (N3+N4) current drainage road, and 2 (N1+N2) are 2.5 times of N1 current drainage road volume.
As can be seen from Figure 6, cold-producing medium is at the top header 220 of the second parallel flow heat crosspoint 200, the bottom header 520 of the 3rd parallel flow heat crosspoint 500, axially flow in the bottom header 120 of the top header 510 and the first parallel flow heat crosspoint 100 and the top header 110, wherein cold-producing medium is at the top header 220 of the second parallel flow heat exchanger unit 100, the top header 510 of the 3rd parallel flow heat crosspoint 500, the axial flow length sum of the top header 110 of the first parallel flow heat crosspoint 100 is N1+N4+N1+N2, bottom header 520 at the 3rd parallel flow heat crosspoint 500, the axial flow length sum of the bottom header 120 of the first parallel flow heat crosspoint 100 is N2+N3+N3+N4, because the length of N1〉length of N3, so N1+N4+N1+N2〉N2+N3+N3+N4.
When being provided with, can make the top header 220 of cold-producing medium in the second parallel flow heat exchanger unit 100, the top header 510 of the 3rd parallel flow heat crosspoint 500, the axial flow length sum of the top header 110 of the first parallel flow heat crosspoint 100 is that the length of N1+N4+N1+N2 is long as much as possible, accounts for the top header 220 of cold-producing medium at the second parallel flow heat crosspoint 200, the bottom header 520 of the 3rd parallel flow heat crosspoint 500, axial more than 70% of length of flow sum in the bottom header 120 of the top header 510 and the first parallel flow heat crosspoint 100 and the top header 110; Cold-producing medium is short as much as possible at the axial flow length sum N2+N3+N3+N4 of the bottom header 120 of the bottom header 520 of the 3rd parallel flow heat crosspoint 500, the first parallel flow heat crosspoint 100, accounts for cold-producing medium axial below 30% of length of flow sum in the bottom header 120 of bottom header 520, top header 510 and the first parallel flow heat crosspoint 100 of the top header 220 of the second parallel flow heat crosspoint 200, the 3rd parallel flow heat crosspoint 500 and top header 110.
Embodiment 5
Parallel flow heat exchanger as shown in Figure 7.Comprise three parallel flow heat exchanger unit that are superimposed, be convenient to describe, it is defined as the first parallel flow heat crosspoint 100, the second parallel flow heat crosspoint 200, the 3rd parallel flow heat crosspoint 500.
The first parallel flow heat crosspoint 100 comprises top header 110, bottom header 120 and the some flat tubes that are arranged in parallel 130 that are communicated with top header 110 and bottom header 120, and the shape of flat tube 130 is with embodiment 1.
The second parallel flow heat crosspoint 200 comprises top header 210, bottom header 220 and the some flat tubes that are arranged in parallel 230 that are communicated with top header 210 and bottom header 220, and the shape of flat tube 230 is with embodiment 1.
The 3rd parallel flow heat crosspoint 500 comprises top header 510, bottom header 520 and the some flat tubes that are arranged in parallel 530 that are communicated with top header 510 and bottom header 520, and the shape of flat tube 530 is with flat tube 130 and 230.
Flat tube 530,230 can be to be connected as a single entity the description in 200610025898.3 inventions as application number with 130, forms three rows of flat pipes.
Part directly is communicated with between the top header 110 and 210 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200, directly is not communicated with between the bottom header 120 and 220 of the first parallel flow heat crosspoint 100 and the second parallel flow heat crosspoint 200.Directly be not communicated with between the top header 210 and 510 of the second parallel flow heat crosspoint 200 and the 3rd parallel flow heat crosspoint 500, part directly is communicated with between the bottom header 220 and 520 of the second parallel flow heat crosspoint 200 and the 3rd parallel flow heat crosspoint 500.The top header 510 of the top header 210 of the top header 110 of such first parallel flow heat crosspoint 100, bottom header 120 and flat tube 130, the second parallel flow heat crosspoint 200, bottom header 220 and flat tube 230, the 3rd parallel flow heat crosspoint 500, bottom header 520 and flat tube 530 constitute the whole heat exchange runner of this embodiment.The import 300 of the heat exchange medium of whole heat exchange runner is arranged on the end tube wall of top header 210 of the second parallel flow heat crosspoint 200, and outlet 400 is arranged on the end tube wall of bottom header 120 of the first parallel flow heat crosspoint 100.
Respectively be provided with a barrier plate 211 and 221 in the top header 210 of the second parallel flow heat crosspoint 200 and bottom header 220, barrier plate 211 and 221 runners with the second parallel flow heat crosspoint 200 are divided into N1 current drainage road and N2+N3 current drainage road; Be provided with a barrier plate 521 in the bottom header 520 of the 3rd parallel flow heat crosspoint 500, barrier plate 521 is divided into N1+N2 current drainage road and N3 current drainage road with the runner in the bottom header 520 of the 3rd parallel flow heat crosspoint 200.
N2+N3 current drainage roads in N3 current drainage road in the top header 110 of the first parallel flow heat crosspoint 100 and the top header of the second parallel flow heat crosspoint 200 210 by the first parallel flow heat crosspoint 100 top header 110 and the opening 129 between the top header 210 of the second parallel flow heat crosspoint 200 link up; N1+N2 current drainage roads in N1 current drainage road in the bottom header 210 of the second parallel flow heat crosspoint 200 and the bottom header of the 3rd parallel flow heat crosspoint 500 510 by the second parallel flow heat crosspoint 200 bottom header 210 and the opening 227 between the bottom header 510 of the 3rd parallel flow heat crosspoint 500 link up, the N3 current drainage roads in the N2+N3 current drainage road in the bottom header 210 of the second parallel flow heat crosspoint 200 and the bottom header 510 of the 3rd parallel flow heat crosspoint 500 by the second parallel flow heat crosspoint 200 bottom header 210 and the opening 229 between the bottom header 510 of the 3rd parallel flow heat crosspoint 500 link up.
The flow direction of cold-producing medium in whole runner is: entered by import 300 in the N1 current drainage road of top header 210 of the second parallel flow heat crosspoint 200, flow to downwards in the N1 current drainage road of bottom header 220 of the second parallel flow heat crosspoint 200 along the flat tube 230 in the N1 current drainage road of the second parallel flow heat crosspoint 200, laterally flow in the N1+N2 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoints 500 by opening 227 again.Flow in the N1+N2 current drainage road of top header 510 that the flat tube 530 of cold-producing medium in the N1+N2 current drainage road of the 3rd parallel flow heat crosspoint 500 in the N1+N2 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoint 500 upwards flow into the 3rd parallel flow heat crosspoint 500, again in the N3 current drainage road of the top header 510 that axially flows to the 3rd parallel flow heat crosspoint 500 of the 3rd parallel flow heat crosspoint 500.Flowing to the flat tube 530 of cold-producing medium in the N3 current drainage road of the 3rd parallel flow heat crosspoint 500 in the N3 current drainage road of top header 510 of the 3rd parallel flow heat crosspoint 500 flows to downwards in the N3 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoint 500.Flow in cold-producing medium in the N3 current drainage road of bottom header 520 of the 3rd parallel flow heat crosspoint 500 laterally flow into the second concurrent flow heat exchange unit 200 by runner pipe 229 the N2+N3 current drainage road of bottom header 220.Flow in the N2+N3 current drainage road of top header 210 that the flat tube 230 of cold-producing medium in the N2+N3 current drainage road of the second concurrent flow heat exchange unit 200 in the N2+N3 current drainage road of bottom header 220 of the second concurrent flow heat exchange unit 200 upwards flow into the second concurrent flow heat exchange unit 200.Flow in cold-producing medium in the N2+N3 current drainage road of top header 210 of the second concurrent flow heat exchange unit 200 laterally flow into the first parallel flow heat crosspoint 100 by opening 129 the N2+N3 current drainage road of top header 110.Flow in cold-producing medium in the N2+N3 current drainage road of top header 110 of the first parallel flow heat crosspoint 100 flow into the first parallel flow heat crosspoint 100 along the top header 110 of the first parallel flow heat crosspoint 100 the N1 current drainage road of top header 110, flat tube 130 in the N1 current drainage road of the first parallel flow heat crosspoint 100 flow into downwards in the N1 current drainage road of bottom header 120 of the first parallel flow heat crosspoint 100 again, is flowed out by outlet 400.
Whole cold-producing medium at flow process through five runners, i.e. N1 current drainage road, N1+N2 current drainage road, N3 current drainage road, N2+N3 current drainage road, N1+N2+N3 current drainage road.Cold-producing medium is in flow process, the volume of five runners progressively increases, the volume that is each runner is: N1 current drainage road<N1+N2 current drainage road<N3 current drainage road<N2+N3 current drainage road<N1+N2+N3 current drainage road, the volume in N1+N2 current drainage road is greater than the 40-50% of N1 current drainage road volume, the volume in N3 current drainage road is greater than the 40-50% of N1+N2 current drainage road volume, the volume in N2+N3 current drainage road is greater than the 40-50% of N3 current drainage road volume, the volume in N1+N2+N3 current drainage road is greater than the 40-50% of N2+N3 current drainage road volume, and N1+N2+N3 is 2.5 times of N1 current drainage road volume.
As can be seen from Figure 7, cold-producing medium is at the top header 220 of the second parallel flow heat crosspoint 200, the bottom header 520 of the 3rd parallel flow heat crosspoint 500, axially flow in the bottom header 120 of the top header 510 and the first parallel flow heat crosspoint 100 and the top header 110, wherein cold-producing medium is at the top header 220 of the second parallel flow heat exchanger unit 100, the top header 510 of the 3rd parallel flow heat crosspoint 500, the axial flow length sum of the top header 110 of the first parallel flow heat crosspoint 100 is N1+N3+N3+N2, bottom header 520 at the 3rd parallel flow heat crosspoint 500, the axial flow length sum of the bottom header 120 of the first parallel flow heat crosspoint 100 is N1+N2+N1, because the length of 2N3〉length of N1, so N1+N3+N3+N2〉N1+N2+N1.
When being provided with, can make the top header 220 of cold-producing medium in the second parallel flow heat exchanger unit 100, the top header 510 of the 3rd parallel flow heat crosspoint 500, the length of the axial flow length sum N1+N3+N3+N2 of the top header 110 of the first parallel flow heat crosspoint 100 is long as much as possible, accounts for the top header 220 of cold-producing medium at the second parallel flow heat crosspoint 200, the bottom header 520 of the 3rd parallel flow heat crosspoint 500, axial more than 70% of length of flow sum in the bottom header 120 of the top header 510 and the first parallel flow heat crosspoint 100 and the top header 110; Cold-producing medium is short as much as possible at the axial flow length sum N1+N2+N1 of the bottom header 120 of the bottom header 520 of the 3rd parallel flow heat crosspoint 500, the first parallel flow heat crosspoint 100, accounts for cold-producing medium axial below 30% of length of flow sum in the bottom header 120 of bottom header 520, top header 510 and the first parallel flow heat crosspoint 100 of the top header 220 of the second parallel flow heat crosspoint 200, the 3rd parallel flow heat crosspoint 500 and top header 110.
3 layers of parallel-flow evaporator performance test curve map that Fig. 8 makes for the present invention.Operating condition of test is as follows among the figure:
Evaporator inlet dry-bulb temperature: 40 ℃;
Evaporator inlet wet-bulb temperature: 27.7 ℃;
Expansion valve inlet temperature: 40 ℃;
Expansion valve inlet pressure: 1.6Mpa;
Evaporator outlet pressure: 0.21Mpa;
The evaporator outlet degree of superheat: 5 ℃.
Result of the test is referring to Fig. 8 and table 1:
Table 1
Air quantity Refrigerating capacity Windage Evaporator outlet dry-bulb temperature Evaporator outlet wet-bulb temperature Flow resistance Refrigerant flow
M 3/h kw pa Mpa Kg/h
Parallel-flow evaporator 283.55 5.372 51.09 6.76 8.04 0.099 154.31
Parallel-flow evaporator 390.7 7.063 77.18 10.88 9.40 0.138 186.86
Parallel-flow evaporator 488.57 8.096 103.36 12.86 11.38 0.174 221.11
By above-mentioned experiment, the parallel-flow evaporator of three stratotype formulas is compared with same size is stacked under identical operating mode and identical air quantity condition, and refrigerating capacity is when air quantity (especially low) quite.
W220 * H240 * T38 that Fig. 9 makes for the present invention, 4 channel parallel flow evaporator device performance test curve maps.Operating condition of test is as follows among the figure:
Evaporator inlet dry-bulb temperature: 38 ℃;
Evaporator inlet wet-bulb temperature: 26.4 ℃;
Expansion valve inlet temperature: 57.2 ℃;
Expansion valve inlet pressure: 1.662Mpa;
Evaporator outlet pressure: 0.193Mpa;
The evaporator outlet degree of superheat: 3 ℃.
Result of the test is referring to Fig. 9 and table 2:
Table 2
Air quantity Refrigerating capacity Windage Evaporator outlet dry-bulb temperature Evaporator outlet wet-bulb temperature Flow resistance Refrigerant flow
M 3/h kw pa Mpa Kg/h
Parallel-flow evaporator 277.74 4.645 52.66 10.04 0.034 0.034 103.62
Parallel-flow evaporator 464.24 7.342 125.53 10.37 0.081 0.081 192.35
Parallel-flow evaporator 554.75 8.431 151.41 10.99 0.086 0.086 209.45
By above-mentioned experiment, W220 * H240 * T38,4 channel parallel flow evaporator devices, it is identical to be equivalent to front face area, and thickness is 60 laminated evaporator.
W242 * H255 * T38 that Figure 10 makes for the present invention, 6 channel parallel flow evaporator device performance test curve maps.Operating condition of test is as follows among the figure:
Evaporator inlet dry-bulb temperature: 27 ℃;
Evaporator inlet wet-bulb temperature: 19.5 ℃;
Expansion valve inlet pressure: 1.52Mpa; Degree of supercooling: 5 ℃;
Evaporator inlet pressure: 1.662Mpa;
The evaporator outlet degree of superheat: 5 ℃.
Result of the test is referring to Figure 10 and table 3:
Table 3
Air quantity Refrigerating capacity Windage Flow resistance
M 3/h kw pa Mpa
Parallel-flow evaporator 450 4.854 116.2 0.123
By above-mentioned experiment, W242 * H255 * T38, the refrigeration of 6 channel parallel flow evaporator devices, it is identical to be equivalent to front face area, and thickness is 69 laminated evaporator.
Parallel flow heat exchanger runner of the present invention can be used for making evaporimeter, especially is used for making the automobile parallel-flow evaporator.Can also be used to making heat pump type air-conditioner heat exchanger.As heat pump type air conditioner evaporimeter and condenser.
More than show and described basic principle of the present invention and principal character and advantage of the present invention.The technical staff of the industry should understand; the present invention is not restricted to the described embodiments; that describes in the foregoing description and the specification just illustrates principle of the present invention; without departing from the spirit and scope of the present invention; the present invention also has various changes and modifications, and these changes and improvements all fall in the claimed scope of the invention.The claimed scope of the present invention is defined by appending claims and equivalent thereof.

Claims (9)

1. parallel flow heat exchanger, the parallel flow heat crosspoint that comprises stack more than at least two, wherein each parallel flow heat crosspoint comprises top header, bottom header that constitutes whole parallel flow heat exchanger runner and the some flat tubes that are arranged in parallel that are communicated with top header and bottom header; Directly be not communicated with between the top header of described adjacent two parallel flow heat crosspoints, and part directly is communicated with mutually between the bottom header of adjacent two parallel flow heat crosspoints; It is characterized in that, described heat exchange medium at described top header along the length of top header axial flow greater than in the length of bottom header along bottom header axial flow, and long as much as possible at described top header along the length of top header axial flow, and at the length only possible weak point of bottom header along bottom header axial flow.
2. parallel flow heat exchanger according to claim 2 is characterized in that the axial flow of heat exchange medium is all finished in the described heat exchanger in the header of top; Heat exchange medium flows and is then all finished through the butt joint of the hole of intercommunication by the bottom header between the parallel flow heat crosspoint of stack; The parallel flow heat exchanger runner then adopts the interior barrier plate of header in the heat exchange unit of stack runner to be divided into a plurality of sections.
3. parallel flow heat exchanger according to claim 1, it is characterized in that, heat exchange medium described top header along the length of top header axial flow account for heat exchange medium described top header along the length of top header axial flow with at length sum 70% or more of bottom header along bottom header axial flow, and heat exchange medium the bottom header along the length of bottom header axial flow account for heat exchange medium described top header along the length of top header axial flow with at length sum 30% below of bottom header along bottom header axial flow.
4. according to claim 1 or 2 or 3 described parallel flow heat exchangers, it is characterized in that, the runner of described heat exchanger is divided into a plurality of sections, along the heat exchange medium flow direction, the channel volume of each section progressively increases, but the channel volume of last section must not be greater than 2.5 times of the channel volume of first section; Preferred version is: the volume of a back section runner is greater than last section channel volume 20-60%.
5. parallel flow heat exchanger according to claim 4 is characterized in that, the volume of a back section runner is greater than last section channel volume 40-50%.
6. parallel flow heat exchanger according to claim 5, it is characterized in that, described last two section runners are provided with the supply mouth of supplemental heat exchange media in these last two sections runners, this supply mouth can design with different shapes, quantity and seat, as long as its former velocity of medium of the not substantive destruction of medium amount that its control replenishes; Wherein the additional heat exchange medium of last runner can be the 15-20% of total heat exchange medium weight.
7. parallel flow heat exchanger according to claim 1 is characterized in that, the import of described heat exchange medium and outlet are arranged on the side pipe wall of top header of a parallel flow heat crosspoint.
8. a parallel flow heat exchanger as claimed in claim 1 can be used for making evaporimeter.
9. a parallel flow heat exchanger as claimed in claim 1 can be used for making the automobile parallel-flow evaporator.
CN2008100425167A 2008-09-04 2008-09-04 Parallel flow heat exchanger and use Expired - Fee Related CN101419002B (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101936670B (en) * 2009-06-30 2013-05-15 王磊 Heat exchanger with micro-channel, parallel-flow and all-aluminum flat pipe welding structure and application
CN103759573A (en) * 2013-12-10 2014-04-30 柳州五菱宝马利汽车空调有限公司 Distributing cavity combined collecting and distributing tube for automotive parallel flow evaporator
CN103759574A (en) * 2013-12-10 2014-04-30 柳州五菱宝马利汽车空调有限公司 Double semilunar split collecting and distributing tube for automotive parallel flow evaporator
CN103759569A (en) * 2013-12-10 2014-04-30 柳州五菱宝马利汽车空调有限公司 Distributing cavity embedded collecting and distributing tube for automotive parallel flow evaporator
CN104160234A (en) * 2012-03-06 2014-11-19 株式会社电装 Coolant evaporator
CN104879955A (en) * 2014-02-27 2015-09-02 杭州三花研究院有限公司 Heat exchanger
CN106196739A (en) * 2016-07-19 2016-12-07 上海交通大学 Arch deflector parallel-flow evaporator
CN106196740A (en) * 2016-07-19 2016-12-07 上海交通大学 U-shaped connector type parallel-flow evaporator
CN113048811A (en) * 2019-12-27 2021-06-29 江苏晨宇科技有限公司 Bending type parallel flow heat exchanger

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101936670B (en) * 2009-06-30 2013-05-15 王磊 Heat exchanger with micro-channel, parallel-flow and all-aluminum flat pipe welding structure and application
CN104160234A (en) * 2012-03-06 2014-11-19 株式会社电装 Coolant evaporator
CN104160234B (en) * 2012-03-06 2016-08-24 株式会社电装 Refrigerant evaporator
CN103759573A (en) * 2013-12-10 2014-04-30 柳州五菱宝马利汽车空调有限公司 Distributing cavity combined collecting and distributing tube for automotive parallel flow evaporator
CN103759574A (en) * 2013-12-10 2014-04-30 柳州五菱宝马利汽车空调有限公司 Double semilunar split collecting and distributing tube for automotive parallel flow evaporator
CN103759569A (en) * 2013-12-10 2014-04-30 柳州五菱宝马利汽车空调有限公司 Distributing cavity embedded collecting and distributing tube for automotive parallel flow evaporator
CN104879955A (en) * 2014-02-27 2015-09-02 杭州三花研究院有限公司 Heat exchanger
CN104879955B (en) * 2014-02-27 2018-10-19 杭州三花研究院有限公司 Heat exchanger
US10330398B2 (en) 2014-02-27 2019-06-25 Hangzhou Sanhua Research Institute Co., Ltd. Heat exchanger
CN106196739A (en) * 2016-07-19 2016-12-07 上海交通大学 Arch deflector parallel-flow evaporator
CN106196740A (en) * 2016-07-19 2016-12-07 上海交通大学 U-shaped connector type parallel-flow evaporator
CN113048811A (en) * 2019-12-27 2021-06-29 江苏晨宇科技有限公司 Bending type parallel flow heat exchanger

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