CN101173841A - Cooling heat exchanger - Google Patents
Cooling heat exchanger Download PDFInfo
- Publication number
- CN101173841A CN101173841A CNA200710167210XA CN200710167210A CN101173841A CN 101173841 A CN101173841 A CN 101173841A CN A200710167210X A CNA200710167210X A CN A200710167210XA CN 200710167210 A CN200710167210 A CN 200710167210A CN 101173841 A CN101173841 A CN 101173841A
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- Prior art keywords
- heat transfer
- transfer plate
- fin
- air
- body portion
- Prior art date
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- 238000001816 cooling Methods 0.000 title claims abstract description 12
- 238000012546 transfer Methods 0.000 claims abstract description 240
- 238000004891 communication Methods 0.000 claims abstract description 24
- 239000012530 fluid Substances 0.000 claims abstract description 16
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 63
- 238000011144 upstream manufacturing Methods 0.000 claims description 22
- 238000007599 discharging Methods 0.000 claims description 4
- 238000012797 qualification Methods 0.000 claims description 3
- 238000005452 bending Methods 0.000 claims 1
- 238000006073 displacement reaction Methods 0.000 claims 1
- 238000009833 condensation Methods 0.000 abstract description 2
- 230000005494 condensation Effects 0.000 abstract description 2
- 239000003507 refrigerant Substances 0.000 description 82
- 230000000052 comparative effect Effects 0.000 description 16
- 238000005219 brazing Methods 0.000 description 15
- 230000000694 effects Effects 0.000 description 11
- 239000008358 core component Substances 0.000 description 6
- 230000005484 gravity Effects 0.000 description 6
- 238000005192 partition Methods 0.000 description 6
- 230000008878 coupling Effects 0.000 description 5
- 238000010168 coupling process Methods 0.000 description 5
- 238000005859 coupling reaction Methods 0.000 description 5
- 239000012071 phase Substances 0.000 description 5
- 238000009825 accumulation Methods 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000005253 cladding Methods 0.000 description 4
- 239000002826 coolant Substances 0.000 description 4
- 238000010438 heat treatment Methods 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 4
- 238000004378 air conditioning Methods 0.000 description 3
- 229910052782 aluminium Inorganic materials 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 239000000306 component Substances 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 239000004411 aluminium Substances 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000000354 decomposition reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000003628 erosive effect Effects 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 229910000906 Bronze Inorganic materials 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000010974 bronze Substances 0.000 description 1
- 239000000498 cooling water Substances 0.000 description 1
- KUNSUQLRTQLHQQ-UHFFFAOYSA-N copper tin Chemical compound [Cu].[Sn] KUNSUQLRTQLHQQ-UHFFFAOYSA-N 0.000 description 1
- 238000005520 cutting process Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 239000006185 dispersion Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
- 230000008719 thickening Effects 0.000 description 1
- 239000012808 vapor phase Substances 0.000 description 1
- 239000003643 water by type Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/03—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits
- F28D1/0308—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other
- F28D1/0325—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another
- F28D1/0333—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with plate-like or laminated conduits the conduits being formed by paired plates touching each other the plates having lateral openings therein for circulation of the heat-exchange medium from one conduit to another the plates having integrated connecting members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
- F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
- F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
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- 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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A cooling heat exchanger has first and second heat transfer plates joined to each other. Each of the first and second heat transfer plates has protrusions protruding from a base portion thereof for defining internal fluid passages, a fin portion projecting from the base portion in the same direction as the protrusions and defining a fin inner space, and an aperture on the base portion at a position corresponding to the fin portion. The fin portion includes an offset wall that is offset from the base portion and connected to the base portion at two positions. The aperture of the first heat transfer plate is displaced from the aperture of the second heat transfer plate with respect to a longitudinal direction of the protrusions so that a communication channel that allows communication between the fin inner spaces of the first and second heat transfer plates is provided for draining condensation.
Description
Technical field
The present invention relates to a kind of cooling heat exchanger, the whole fin part that forms on heat transfer plate with heat transfer plate.
Background technology
For example, the open No.2002-147983 of pending trial Japan Patent has described a kind of board-like cooling heat exchanger, evaporimeter for example, and it is made of heat transfer plate, uses the fin component that separates.Heat transfer plate comprises generally flat body portion, protrudes to limit the projection of internal fluid channels from body portion, and for example the internal flow of cold-producing medium flows through from described internal fluid channels.For example make protrusion form described projection by extruding.Heat transfer plate has in addition at the slit fin that reaches on the body portion between the projection.
In disclosed heat exchanger, between the external fluid of for example air of its flows outside and internal flow, implement heat exchange.Simultaneously, air stream is by protruding disturbance.Just, because projection as the turbulent flow parts that cause turbulent flow, has therefore improved the heat transfer coefficient of air.In addition, improved heat transfer efficiency.And fin has roughly U shape cross section, thereby air can flow in fin.Because the structure of fin causes the heat transfer area of air is increased, thereby the formula heat transfer efficiency advances a raising.
Although this plate heat exchanger does not have the fin component that is used in usually in fin and the tube type heat exchanger, wave-shaped fins for example, heat transfer efficiency is enhanced by the slit fin.Through the formed heat transfer plate of extruding, form plate heat exchanger by brazing simply.
In cooling heat exchanger,, air produces condensation owing to being cooled off.The condensed water (condensate liquid) that is produced on the heat exchanger plate surface is easy to be accumulated in the inboard of slit fin.In this case, because water is present in slit fin inner surface and by between the air of slit fin, therefore the thermal resistance that causes owing to water increases probably.The result is that heat transfer efficiency reduces.Also have, because air pressure, the condensed water of accumulation will be dispersed to the downstream position with respect to air-flow.Just, in cooling heat exchanger, need from fin component, to release effectively or discharge condensed water.
Summary of the invention
Consider that afore-mentioned makes the present invention, the purpose of this invention is to provide the cooling heat exchanger that can improve the discharging of condensed water.
According to an aspect of of the present present invention, the heat exchanger that is used to cool off at the air of its flows outside comprises first heat transfer plate and second heat transfer plate.Each first and second heat transfer plate comprises body portion and a plurality of projection of qualification along the plane of air-flow direction, and described a plurality of projectioies are protruded and extended in the direction that intersects with air-flow direction from body portion.First and second heat transfer plates are connected to each other, so that its body portion contacts with each other.And the projection of first heat transfer plate is projection in one direction, and the projection of second heat transfer plate is protruding in the opposite direction.The inner flow passage that described projection is provided for making internal flow to flow therein.Each first and second heat transfer plate further comprises the fin part of protruding in the direction identical with each projection from body portion that is used to limit space in the fin, and is in the hole on the body portion in the position corresponding to the fin part.Each fin partly comprises from the skew wall of body portion skew.The skew wall is connected to body portion two positions, and described two positions are spaced apart on the direction of the longitudinal direction that is parallel to projection.Longitudinal direction with respect to projection, the hole of first heat transfer plate is away from the hole of second heat transfer plate, and in the fin of first heat transfer plate in the fin of space and second heat transfer plate space be connected, the feasible communication passage that is used to discharge condensed water is set between first and second heat transfer plates.
Thereby the condensed water in the fin in the space is discharged smoothly by communication passage.
According to another aspect of the present invention, the heat exchanger that is used to cool off air comprises first heat transfer plate and second heat transfer plate.First heat transfer plate comprises body portion, a plurality of projection, fin part and first hole, described body portion limits the plane along air-flow direction, described a plurality of projection is protruded from body portion, described fin part on the direction identical with a plurality of projectioies from body portion protrude so that in the fin space be limited at the inside of fin part, described first hole on body portion corresponding to the position of fin part.Described projection is extended on the direction that intersects with air-flow direction and is defined for the internal fluid channels that makes fluid flow inside therein.Fin partly comprises from the skew wall of body portion skew.The skew wall is connected to body portion in two positions that the longitudinal direction along projection separates.Second heat transfer plate comprises that qualification is along the body portion on the plane of air-flow direction, from a plurality of projectioies and second hole that body portion protrudes.Projection in second heat transfer plate is extended on the direction that intersects with air-flow direction, and limits the internal fluid channels that allows fluid flow inside therein.First heat transfer plate and second heat transfer plate are connected to each other, so that its body portion is in contact with one another.Projection in first heat transfer plate is protruded in one direction, and the projection of second heat transfer plate is protruded in the opposite direction.With respect to the longitudinal direction of projection, overlap at least in first hole and second hole.
Therefore, because the external communications of first and second holes and first and second heat transfer plate is passed through in the interior space of fin, so condensed water will be discharged by first and second hole from space in the fin.Like this, just discharged condensed water effectively.
Description of drawings
According to detailed description with reference to the accompanying drawings, other purpose of the present invention, characteristics and advantage will become clearer, and same parts is marked by same reference numbers in the accompanying drawing, in the accompanying drawing:
Fig. 1 is the decomposition diagram according to the evaporimeter of first embodiment of the invention;
Fig. 2 is according to the decomposition diagram of the evaporimeter of first embodiment, is used to explain cold-producing medium overall flow therein;
Fig. 3 is the cross-sectional view along the evaporimeter of Fig. 1 center line III-III intercepting;
Fig. 4 is the perspective view according to the part of the heat transfer plate of the evaporimeter of first embodiment;
Fig. 5 is the cross-sectional view along the heat transfer plate of Fig. 4 center line V-V intercepting;
Fig. 6 is the schematic cross section of the heat transfer plate of example as a comparison;
Fig. 7 A is the chart that shows each fin condensed water cumulant in the comparative example;
Fig. 7 B is the chart of demonstration according to each fin condensed water cumulant of the evaporimeter of first embodiment;
Fig. 8 is the chart that concerns between the condensed water cumulant that shows according to the fin height of first embodiment and comparative example and each fin;
Fig. 9 is the schematic cross section according to the part of the heat transfer plate of the evaporimeter of second embodiment of the invention;
Figure 10 is the schematic cross section according to the part of the heat transfer plate of the evaporimeter of third embodiment of the invention;
Figure 11 is the schematic cross section according to the part of the heat transfer plate of the evaporimeter of fourth embodiment of the invention;
Figure 12 is the schematic cross section according to the part of the heat transfer plate of the evaporimeter of fifth embodiment of the invention;
Figure 13 is the schematic cross section according to the part of heat transfer plate in the evaporimeter of sixth embodiment of the invention; With
Figure 14 is the schematic cross section according to the part of the heat transfer plate of the evaporimeter of seventh embodiment of the invention.
The specific embodiment
Now, will will first to the 7th embodiment of the present invention be described with reference to the accompanying drawings.In second to the 7th embodiment, will be indicated with the similar parts of parts among first embodiment by same reference numbers, and will no longer describe.
(first embodiment)
Used by evaporimeter 10 exemplarily referring to figs. 1 to the heat exchanger of 8, the first embodiment as auto air-con.Heat exchanger described in the general structure of evaporimeter 10 and the USP6047769 (Japanese laid-open patent publication number No.11-287580) is similar.Evaporimeter 10 is total comprises a plurality of heat transfer plates 12.
Among the figure, arrow A 1 expression is used for the overall flow direction as the air of external fluid of air conditioning operation, arrow B is represented for example overall flow direction of the internal flow of cold-producing medium, flows in the internal fluid channels of described internal flow in being formed on heat transfer plate.The flow direction B of cold-producing medium and the flow direction A1 of air intersect.In the example shown, evaporimeter 10 is constructed to the vertical convection heat exchanger, and wherein the flow direction A1 of air is haply perpendicular to the flow direction B of cold-producing medium.And evaporimeter 10 is configured the flow direction A1 that makes with respect to air, and the cold-producing medium upstream passages that is connected with refrigerant inlet is positioned in the downstream of the cold-producing medium downstream passages that is connected with refrigerant outlet.
Evaporimeter has core 11, is used to implement the heat exchange between air and the cold-producing medium.Construct core 11 by stacked a plurality of heat transfer plates 12 on the direction of approximate vertical air-flow direction A1.Heat transfer plate 12 comprises case slot part 20 to 23 with lower end in the top.Because air is by case slot part 20 to 23, so core 11 is made of the intermediate member of the heat transfer plate 12 of removing case groove 20 to 23.
By extruding metal sheet parts, form each heat transfer plate 12.For example, plate member is the cladding sheet with matrix material of being made by A3000 aluminium, and two surfaces of described cladding sheet have been coated with A4000 aluminum bronze wlding material.Heat transfer plate 12 is extremely thin plate, and has thickness t, as shown in Figure 3.In the present embodiment, for example, the thickness t of heat transfer plate 12 is 0.2mm.Heat transfer plate 12 has essentially rectangular plate shape.All heat transfer plates 12 roughly have same external dimensions.
As shown in Figure 3, each heat transfer plate 12 has the generally flat body portion 13 of common plane and the projection of protruding from described body portion 13 14.For example, the extruding by for example mold pressing processing or protrusion processing forms projection 14.The longitudinal direction that projection 14 is formed rib and is parallel to heat transfer plate 12 extends continuously.
In the example shown in Fig. 3, each projection 14 has roughly semi-circular cross-section.Yet projection 14 can have any other shape of cross section, for example has the roughly trapezoidal shape of fillet etc.
For example, evaporimeter 10 is set so that in use the longitudinal direction of heat transfer plate 12 corresponding to gravity direction, i.e. above-below direction.Therefore, projection 14 extends upward at upper and lower.In other words, projection 14 is hung down and is extended as for air-flow direction A1.
In addition, fin 17 is arranged on the above-below direction with predetermined space.In the example shown in Fig. 3,4, fin 17 is formed a row on above-below direction, and between two adjacent protrusion 14.Yet fin 17 can be formed between two adjacent protrusion 14 by many rows or interlace mode.
In the example shown in Fig. 4, each skew wall 17a is parallel to the plane of body portion 13.The upper and lower side of skew fin 17a is connected to body portion 13 by sidewall 17b, 17c.Thereby each fin 17 has roughly U shape.
As shown in Figure 3, for example, the height of projection of skew wall 17a is that the fin height Fh of fin 17 is roughly the same or slightly less than rib heights Rh with the rib heights Rh of projection 14.
In addition, fin 17 has fin inside dimension Fhi, and described Fhi determines (that is, Fhi=Fh-t) by the thickness that deducts heat transfer plate 12 from fin height Fh.Fin inside dimension Fhi makes the width in the space that air passes through corresponding to being used to of limiting between the plane of body portion 13 and the skew wall 17a, just, the size between the plane of the inner surface of skew wall 17a and body portion 13 on perpendicular to the direction on the plane of body portion 13.Fin 17 has fin width Fw with respect to air-flow direction A1.
For example, each fin 17 is manufactured in following mode.At first, two slits are formed on the body portion 13, have the interval corresponding to fin width Fw.Then, the part between two slits is protruded.Thereby fin 17 has roughly U shape.
In this case, described part is protruded, so that each sidewall 17b, 17c are tilted predetermined angle theta with respect to the surface of body portion 13.In addition, has fillet, promptly so-called R shape between each sidewall 17b, 17c and body portion 13 and the skew wall 17a.Therefore, fin 17 has level and smooth protrusion shape.Just, the structure of fin is enhanced.
Consider the structure of fin 17, for example, fin width Fw is equal to or greater than 0.2mm, and relative air-flow direction A1, and the fin pitch between the two adjacent fins 17 is equal to or greater than 0.4mm from Fd.
The roughly U shape of fin 17, just, the shape of slit fin is corresponding to the otch of otch or opening being provided on body portion 13 and removing shape.Just, by forming fin 17, cutting opening (after this, abbreviating the hole as) 17d is formed on the body portion 13 in the position corresponding to fin 17 by forming fin 17.
In the present embodiment, for example, the length G of hole 17d, just, the size of hole 17d equals to obtain greater than 5mm on above-below direction.Here, in Fig. 5, the size G of hole 17d comprises the size that is formed on the fillet between body portion 13 and sidewall 17b, the 17c.
Yet if the erosion of body portion 13 is continued, cold-producing medium will leak from fin 17.Leak in order to limit owing to corroding the cold-producing medium cause, body portion 13 is equal to or greater than 0.3mm (that is Bw-Fw 〉=0.3mm), with respect to the difference of the size Bw of air-flow direction A1 and fin width Fw.
In other words, on each side of fin 17 with respect to the size of the body portion 13 of air-flow direction A1 (promptly, when the width of each sidepiece of body portion 13 on the opposite side of fin 17) being equal to or greater than 0.15mm (as the surplus that corrodes), because the cold-producing medium that the erosion of body portion 13 causes leaks minimizing fully.
Equally, in order fully to keep the brazing of body portion 13, the difference of the size Bw of body portion 13 and fin width Fw for example is equal to or greater than 1.0mm.Just, with respect to air-flow direction A1, when being equal to or greater than 0.5mm, body portion 13 is by brazings fully in the overlapping dimension (for example, contact size or brazing edge) of the body portion 13 of each side of fin 17.
In the present embodiment, the length of fin 17, promptly fin 17 with respect to the size of above-below direction greater than fin width Fw with respect to air-flow direction A1.Just, fin 17 has the length on above-below direction.
As shown in Figure 5, with respect to above-below direction, the position of fin 17 is shifted between first and second heat transfer plate 12 or staggers, so that the 17d part, hole of the hole 17d of first heat transfer plate 12 and second heat transfer plate 12 is overlapping.Just, the hole 17d of first heat transfer plate 12 is connected with the hole 17d of second heat transfer plate 12 partly.
Because the hole 17d in first and second heat transfer plate 12 is overlapped, allow the continuous communication passage P that is communicated with between the inner space of fin 17 on the above-below direction so be formed on.In example shown in Fig. 5, communication passage P is formed on the above-below direction continuously.Yet communication passage P is continuously always necessary on heat transfer plate 12 length.Connected space P can suitably be separated on above-below direction.
In Fig. 1,2,, fin 17 is not shown for illustrated simplification.In the example shown in Fig. 1 to 3, each heat transfer plate 12 has five projectioies 14.Yet, the quantity of the projection 14 of each heat transfer plate 12, promptly the quantity of refrigerant passage 15,16 can change according to service condition, for example desired properties, outer shape or the like.
Also have, each heat transfer plate 12 has in the top box channel parts 20,22 of upper end with in two nowel channel parts 21,23 of lower end.Top box channel parts 20,22 is roughly alignd along air-flow direction A1.Similarly, nowel channel parts 21,23 is roughly alignd along air-flow direction A1.Top box channel parts 20,22 and nowel channel parts 21,23 are separated on flow of refrigerant direction B.After this, top box channel parts 20 is also referred to as air downstream top box channel parts 20, nowel channel parts 21 also is called as air downstream nowel channel parts 21, and top box channel parts 22 also is called as air upstream side top box channel parts 22 and nowel channel parts 23 also is called as air upstream side nowel channel parts 23.
Here, the height of projection of case channel parts 20 to 23 comprises the thickness t of heat transfer plate 12.As shown in Figure 3, tube coupling is the arrangement pitch of paired heat transfer plate 12 apart from Tp.In addition, space pitch Sp for the determined numerical value of thickness t that deducts two heat transfer plates 12 from tube coupling apart from Tp (that is, Sp=Tp-2t).
Among Fig. 3, as an example, 14 rib heights Rh is less than tube coupling half apart from Tp for projection, that is, and and less than the height of projection of case channel parts 20 to 23.Yet rib heights Rh can be changed.For example, projection 14 rib heights Rh can equal or haply slightly greater than the height of projection of case channel parts 20 to 23.
The space that is limited by air upstream side top box channel parts 22 and air downstream top box channel parts 20 is spaced mutually.That is, air upstream side top box channel parts 22 and air downstream top box channel parts 20 provide the refrigerant passage part dividually.Similarly, the space that is limited by air upstream side nowel channel parts 23 and air downstream nowel channel parts 21 is spaced mutually.That is, air upstream side nowel channel parts 23 and air downstream nowel channel parts 21 provide the refrigerant passage part dividually.
Each case channel parts 20 to 23 roughly is formed with open communication 20a to 23a in the pars intermedia office at it.Be applied so that the end of case channel parts 20 to 23 when contacting with each other between phase adjacency pair heat transfer plate 12, is interconnected by opening 20a to 23a by each case channel parts 20 to 23 space that limited at paired heat transfer plate 12.
Therefore, the stack of plates direction with respect to the roughly left and right directions among Fig. 1,2 is for example interconnected between adjacent heat transfer 12 by case channel parts 20 to 23 refrigerant passage that limited.In other words, four case slot spaces are provided by case channel parts 20 to 23 respectively on the stack of plates direction.
In addition, as shown in Figure 3, the position of projection 14 is staggered between the phase adjacency pair at heat transfer plate 12 on the air-flow direction A1.Therefore, the projection 14 of a pair of heat transfer plate 12 is relative with the body portion 13 of adjacent a pair of heat transfer plate 12.In the example shown in Fig. 3, the projection 14 of a pair of heat transfer plate 12 is positioned as the centre position corresponding to the body portion 13 of adjacent a pair of heat transfer plate 12.Just, the projection 14 of a pair of heat transfer plate 12 is positioned as the center corresponding to the rib pitch Rp of adjacent a pair of heat transfer plate 12.
As mentioned above, projection 14 rib heights Rh is roughly tube coupling apart from half of Tp.Therefore, on the stack of plates direction, the gap is arranged between the body portion 13 of the top of projection 14 of a pair of heat transfer plate 12 and adjacent a pair of heat transfer plate 12.
Like this, between adjacent paired heat transfer plate 12, on air-flow direction A1, on the width of heat transfer plate 12, form air flue 18 continuously.As by shown in the arrow A among Fig. 32, air can flow through air duct 18 with tortuous or sinuous mode.In air flue 18, fin 17 bump, adjacent 14 are positioned.
In the example shown in Fig. 3, fin 17 is positioned in the center of the rib pitch Rp of body portion 13, just, is positioned at the upward mid portion between the adjacent protrusion 14 of air-flow direction A1.Therefore, preset distance X is relative at interval for the outer surface of the projection 14 that the outer surface of the skew wall 17a of each fin 17 is adjacent with skew wall 17a with striding air flue 18.
Although do not illustrate, heat transfer plate 12 has strides the contact rib that air flue 18 protrudes to adjacent heat transfer 12 from body portion 13.Described contact rib is the small embossment form, has level and smooth semi-circular shape, and protrudes from body portion 13 and the position between fin 17.
The contact rib has haply the identical height of projection of rib heights Rh with projection 14.The top of the projection 14 of another heat transfer plate 12 that the contact rib of a heat transfer plate 12 is adjacent with striding air flue 18 contacts.Contact with the top of the projection 14 of adjacent heat transfer and on the stack of plates direction extruding force imposed under the state that contacts the contact portion between rib and protruding 14 at the contact rib, evaporimeter 10 is by whole brazing.
Locate to implement brazing under the state of contact owing to forming the centre position of refrigerant passage 15,16 in adjacent heat transfer 12, except case channel parts 20 to 23, body portion 13 is by brazings fully.Because leaking from refrigerant passage 15,16 owing to the cold-producing medium that not enough brazing causes by fully brazing, seldom appears in heat transfer plate 12.
For the body portion 13 of abundant transmission of heat by contact plate 12, the contact rib forms on the longitudinal direction of heat transfer plate 12 dividually and in a plurality of positions.
Next, will the import of cold-producing medium and the structure of spout member be described.As shown in Fig. 1,2, evaporimeter 10 has first end plate 24, second end plate 25 in heat transfer plate 12 ends of piling up.First end plate 24, second end plate 25 the has size identical with heat transfer plate 12.Each first end plate 24, second end plate 25 have roughly writing board shape.First end plate 24, second end plate 25 are connected to the end of heat transfer plate 12, so that its inner surface contacts the surface of the formation case channel parts 20 to 23 of first end plate 24, second end plate 25.
Vapour-liquid two-phase, the low pressure refrigerant by the decompression of pressure regulating equipment (not shown) flows in refrigerant inlet pipe 24a.On the other hand, refrigerant outlet pipe 24b is connected with the suction side of compressor (not shown).Therefore, the vapor phase refrigerant that has been evaporated in evaporimeter 10 is introduced compressor from refrigerant outlet pipe 24b.
The air downstream refrigerant passage 15 that is limited between the projection 14 of paired heat transfer plate 12 is connected with refrigerant inlet pipe 24a.Cold-producing medium from refrigerant inlet pipe 24a flows in air downstream refrigerant passage 15.Thereby air downstream refrigerant passage 15 is provided at the inlet side refrigerant passage in the whole evaporimeter 10.
On the other hand, air upstream side refrigerant passage 16 is connected with refrigerant outlet pipe 24b.Be that the cold-producing medium of inlet side refrigerant passage flows in air upstream side refrigerant passage 16, flowed out evaporimeter 10 from refrigerant outlet pipe 24b then by air downstream refrigerant passage 15.Therefore, air upstream side refrigerant passage 16 provides the outlet side refrigerant passage.
Cold-producing medium roughly flows through evaporimeter 10, shown in arrow P a to Pk among Fig. 2.In this case, air downstream top box channel parts 20 provides refrigerant inlet side top box slot space, and air downstream nowel channel parts 21 provides refrigerant inlet side nowel slot space.Equally, air upstream side top box channel parts 22 provides refrigerant outlet side top box slot space, and air upstream side nowel channel parts 23 provides refrigerant outlet side nowel slot space.
Although do not show that partition member is set at the pars intermedia office of piling up of heat transfer plate 12, so that piling up of heat transfer plate 12 roughly is divided into left half (first) Y1 and right half (second portion) Y2.Thereby the refrigerant inlet side top box slot space that is provided by air downstream top box channel parts 20 is divided into left path space and right path space by partition member.Similarly, the refrigerant outlet side case slot space that is provided by air upstream side top box channel parts 22 is divided into left path space and right path space by partition member.
For example, by opening 22a, the 22a structure partition member of heat transfer plate 12 in the middle of closed, described middle heat transfer plate 12 is positioned in the centre of piling up of heat transfer plate 12.
In evaporimeter 10, at first, the vapour-liquid two phase refrigerant flows into refrigerant inlet side case slot space from refrigerant inlet pipe 24a, as by shown in the arrow P a.Because refrigerant inlet side case slot space is divided into left path space and right path space by partition member, so cold-producing medium only flows into the left path space of refrigerant inlet side case slot space.
Thereby cold-producing medium flows through the inlet side refrigerant passage of left half Y1 on the downward direction shown in arrow P b, and then the refrigerant inlet side nowel slot space that is provided by air downstream nowel channel parts 21 is provided.In refrigerant inlet side nowel slot space, cold-producing medium is moving to the right upper reaches, just, and towards right half Y2, as by shown in the arrow P c.
Thereby by making progress upward shown in the arrow P d, cold-producing medium flows through the inlet side refrigerant passage 15 among the right half Y2, and then flows in the right path space of refrigerant inlet side top box slot space.The opening 20a of the air downstream top box channel parts 20 of rightmost heat transfer plate 12 is connected by the communication paths (not shown) on the top that is formed on second end plate 25 with the opening 22a of upstream side top box channel parts 22.
Therefore, as by shown in the arrow P e, moving of the right path space of cold-producing medium in refrigerant inlet side top box slot space to the right upper reaches, then, as flow into the right path space of refrigerant outlet side top box slot space by the communication paths of passing through right end plate 25 shown in the arrow P f.
Because refrigerant outlet side top box slot space is divided into left path space and right path space by partition member, cold-producing medium only flows into the right path space of refrigerant outlet side top box slot space from communication paths, as by shown in the arrow P g.Then, cold-producing medium flows through the outlet side refrigerant passage 16 of right half Y2, with as by the downward direction shown in the arrow P h.As by shown in the arrow P i, cold-producing medium flows into refrigerant outlet side nowel slot space, and then moving to the right upper reaches.
After this, cold-producing medium flows through the outlet side refrigerant passage 16 of left half Y1, with as by shown in the arrow P j upward to, and then flow in the left path space of refrigerant inlet side top box slot space.As by shown in the arrow P k, refrigerant flow direction refrigerant outlet pipe 24b, and flow out from evaporimeter 10.
When making evaporimeter 10, for example the building block of heat transfer plate 12, first end plate 24, second end plate 25 and refrigerant inlet pipe 24a, refrigerant outlet pipe 24b is assembled, to realize contact at predetermined portions.The building block of assembling uses predetermined anchor clamps to be maintained under the above-mentioned state and is placed in the stove.When the building block of being assembled was heated to the fusing point of brazing material, each building block was by whole brazing.Thereby evaporimeter 10 is by whole brazing.
Next, will the operation of evaporimeter 10 be described.For example, evaporimeter 10 is accommodated in the air-conditioning unit housing (not shown), so that above-below direction is that the longitudinal direction of heat transfer plate 12 is corresponding to vertical direction among Fig. 1,2.When the pressure fan (not shown) that is used for the air conditioning operation was activated, air passed through evaporimeter shown in arrow A 1.
When the compressor of cold-producing medium circulation was operated, the vapour-liquid two phase refrigerant was introduced evaporimeter 10 by the pressure regulating equipment from for example expansion valve.Thereby cold-producing medium passes through evaporimeter 10 shown in arrow P a to Pk.
Because air flue 18 is formed between the heat transfer plate 12, the air that blows by pressure fan flows through air flue 18 in the mode of wriggling shown in arrow A 2.Simultaneously, come vaporized refrigerant by the latent heat that from air, receives evaporation, and then air is cooled.
In this case, with respect to air-flow direction A1, inlet side refrigerant passage 15 is set at the downstream of outlet side refrigerant passage 16.Therefore, the arrangement of the import of cold-producing medium and outlet is opposite with air stream.Just, total flow direction of cold-producing medium is opposite with total airflow direction.
Airflow direction A1 is substantially perpendicular to the longitudinal direction of projection 14.Projection 14 provides the heating surface that protrudes from body portion 13 and intersect with air-flow direction A1.Thereby air-flow is hindered by projection 14 and is disperseed.In view of the above, the heat transfer coefficient of air is enhanced on the heating surface of projection 14.
In the heat-exchangers of the plate type that core component is constructed by heat transfer plate, the heating surface of air is less than the air heating surface of fin and tube type heat exchanger, and the core is by pipe and fin structure in described fin and tube type heat exchanger.Therefore, be difficult to the heat transfer property that keeps essential fully usually.
In the evaporimeter 10 of present embodiment, fin 17 is formed on the heat transfer plate 12.Fin 17 have roughly the U shape and be set between the adjacent protrusion 14 and air flue 18 in.Compare with the heat-exchangers of the plate type that does not have fin, because air is mobile along inner surface and the outer surface of skew wall 17a, so heat transfer surface area increases.
In addition, at body portion 13 places owing to fin 17 has improved the air heat transfer coefficient.For example, under fin was not formed on situation on the body portion 13, with respect to airflow direction A1, temperature boundary layer position was downstream made progress forward and thickening.Thereby the air heat transfer coefficient on the body portion 13 may be reduced.
On the other hand, in the present embodiment, because fin 17 is formed on the body portion 13 between the adjacent protrusion 14, so the temperature boundary layer thickness on the flat surfaces of body portion 13 is reduced.Therefore, compare, improve at body portion 13 place's air heat transfer coefficients with the body portion 13 that does not have fin 17.
Therefore, even in heat-exchangers of the plate type, heat transfer efficiency is improved effectively, has suppressed the increase of flow impedance simultaneously.
In the present embodiment, sidewall 17b, the 17c of fin 17 is with respect to the plane θ inclination at a predetermined angle of body portion 13, so that structure fin 17.Yet, comparing perpendicular to the situation of body portion with fin side wall, the length FL of the skew wall 17a on above-below direction is reduced.Therefore, the length FL owing to skew wall 17a reduces to cause heat transfer efficiency to be lowered.
Thereby for the structure that improves fin 17 and improve heat transfer efficiency, for example, the pre-determined tilt angle θ of each sidewall 17b, 17c can be set at and be equal to or greater than 30 degree and be equal to or less than in the scopes of 60 degree.
Here, the length FL of skew wall 17a is the size of the flat of the skew wall 17a inner surface on above-below direction.Just, the length FL of skew wall 17a does not comprise the size that is formed on the fillet between skew wall 17a and sidewall 17b, the 17c.
Next, will the effect of the condensed water of draining evaporimeter 10 be described.In evaporimeter 10, because cooling effect, airborne moisture is by condensing, and then the generation condensed water.Condensed water tends to be accumulated in the inside of fin 17, particularly at the interior zone of lower wall 17c, as by among Fig. 5 shown in the regional M.
Fig. 6 shows comparative example, and wherein the fin 17 of first and second heat transfer plates 12 is set at same position with respect to following direction.In this comparative example, condensed water is stopped by lower wall 17c.Therefore, the discharging of condensed water is restricted.In other words, condensed water is received by lower wall 17c.
In the present embodiment shown in Fig. 5, on the other hand, staggering between the heat transfer plate 12 on the above-below direction in pairs in the position of fin 17, so that communication passage P is formed in the fin 17 continuously.Therefore, smoothly flow downward by communication passage P, as by shown in the arrow N, and not stopped by lower wall 17c at the inboard condensed waters that produce of fin 17.In other words, the discharge-channel that is used to discharge condensed water is provided by communication passage P.Therefore, condensed water is discharged effectively.
In addition, be 5mm or when bigger, condensed water is more effectively discharged at the size G of the hole of fin 17 17d at above-below direction.
Because sidewall 17b, 17c and body portion 13 form fillet, connected space P is formed the smooth curved shape.Therefore, condensed water is discharged smoothly.
Fig. 7 A is the chart of the condensed water cumulant of each fin of demonstration comparative example.Fig. 7 B is for showing the chart of the condensed water cumulant of each fin in the present embodiment.As shown in Fig. 7 A, 7B, the cumulant of each the fin condensed water in the present embodiment be roughly each the fin condensed water in the comparative example cumulant half or 1/3rd.
Fig. 8 shows the chart that concerns between the cumulant of fin height Fh and each fin condensed water.Trunnion axis is represented fin height Fh, and vertical axis is represented the cumulant of each fin condensed water.In this case, fin width Fh is 1.5mm.
Shown in the curve among Fig. 8, during less than 0.35mm, the condensed water cumulant of each fin 17 is greater than the condensed water cumulant of each fin 17 in the comparative example in the present embodiment at fin height Fh.This is caused by following reason.
In the present embodiment, be limited at the width of the communication passage P between body portion 13 and the skew wall 17a, promptly communication passage P equals fin height Fh haply hanging down as for the size on the direction on the plane of body portion 13.As shown in Figure 5.On the other hand, in comparative example, be limited at the width in the space between the fin 17, promptly the space that condensed water stops on hanging down as for the direction on the plane of body portion 13 is (after this, be called condensed water accumulation space) be the twice of fin height Fh, as shown in Figure 6.
In the present embodiment, if fin height Fh less than the height of necessity, then condensed water can not flow through communication passage P easily.Therefore, in whole communication passage P, flowing of condensed water will be stagnated, although condensed water can only not be accumulated in the topmost of communication passage P.
In comparative example, because the width in condensed water accumulation space is greater than the width of communication passage P in the present embodiment.Therefore, condensed water can not be accumulated in the top in each condensed water accumulation space.The result is, the condensed water cumulant of each fin is relatively less than the condensed water cumulant of each fin in the present embodiment in the comparative example.
Therefore, during less than 0.35mm, each the fin condensed water cumulant in the present embodiment is greater than each the fin condensed water cumulant in the comparative example at fin height Fh.On the other hand, when fin height Fh was equal to or greater than 0.35mm, each the fin condensed water cumulant in the present embodiment was less than each the fin condensed water cumulant in the comparative example.Thereby, improved the emission effect in the present embodiment.
In the present embodiment, the thickness of heat transfer plate 12 is 0.2mm.Therefore, be 0.35mm or more for a long time, fin inner height Fhi is equal to or greater than 0.15mm at fin height Fh.In other words, when the width that is limited at the space between skew wall 17a and the body portion 13 was equal to or greater than 0.15mm, the condensed water cumulant of each fin was less than the condensed water cumulant of each fin in the comparative example in the present embodiment.Therefore, improved emission effect.
Top idea can be employed with the gap between the surface of skew wall 17a that sets fin 17 and heat transfer plate 12.For example, at the outer surface of skew wall 17a with stride when distance X is equal to or greater than 0.15mm between the outer surface of the relative projection 14 of air flue 18 and fin 17, the cumulant of the condensed water in the described gap will be reduced.Like this, improved emission effect.
In Fig. 7 A, 7B and 8, measure the cumulant of condensed water below under the condition.
(1) outside dimension of the evaporimeter in present embodiment and the comparative example: width is 260mm; Highly be 215mm; And the degree of depth is 38mm.Here, width is the size on the stack of plates direction, shown in arrow W among Fig. 2.Highly be by the size shown in the arrow H among Fig. 2.In addition, the degree of depth is the size of air-flow direction A1, shown in arrow D among Fig. 2.
(2) volume of air is 500m
2/ h.The resistance that air at the core component place flows equates in the evaporimeter of present embodiment and comparative example.
(3) for comparative example, the thickness t of heat transfer plate is 0.15mm; Space pitch Sp is 2.6mm; Rib pitch Rh is 7.1mm; And height of projection Rh is 1.45mm.
(4) for the evaporimeter in the present embodiment, the thickness t of heat transfer plate 12 is 0.15mm; Space pitch Sp is 3.0mm; Rib pitch Rp is 7.1mm; Height of projection Rh is 1.45mm, and fin height Fh is 1.0mm; And fin width Fw is 0.8mm.Here, fin pitch Fp is half of rib pitch Rp.
In example shown in Figure 3, heat transfer plate 12 has fin 17 with respect to air-flow direction A1 in the downstream of downstream projection 14.Yet, not necessarily always need have fin 17 in the downstream of downstream projection 14 with respect to air-flow direction A1.
Be not set at respect to air-flow direction A1 in the situation in downstream of downstream projection 14 at fin 17, even the condensed water in the fin 17 is blown away by air pressure, the condensed water that is blown is discharged attached sticking on the projection 14 that is positioned in fin 17 downstreams and along protruding 14 with downward direction.Therefore, the dispersion of the condensed water in the fin 17 will be reduced.
In the present embodiment, heat transfer plate 12 has smooth basically shape, and projection 14, fin 7, case channel parts 20 to 23 etc. are formed from flat wall to be protruded.Just, body portion 13 is a coplane.Yet body portion 13 coplanes are not necessarily always essential.Selectively, except the mid portion of the heat transfer plate 12 of case channel parts 20 to 23, the part that promptly forms the heat transfer plate 12 of core component 11 can have wave-like, and it comprises the smooth curved wall, to replace flat wall.Equally in this case, will provide similar effect as present embodiment.
(second embodiment)
Except the structure of skew wall 17a, the evaporimeter 10 of foundation second embodiment is similar to the evaporimeter 10 among first embodiment.In first embodiment, skew wall 17a is parallel to the plane of body portion 13.On the other hand, in a second embodiment, with respect to above-below direction, skew wall 17a tilts with respect to the plane of body portion 13.
As shown in Figure 9, each skew wall 17a tilts with predetermined angle θ a with respect to the plane of body portion 13, so that distance increases to upper position between the plane of skew wall 17a and body portion 13.Like this, the condensed water in the fin 17 of a heat transfer plate 12 is introduced in the fin 17 of relative heat transfer plate 12 smoothly, as by as shown in the arrow N.Therefore, condensed water is by further level and smooth discharging.
(the 3rd embodiment)
Except the structure of skew wall 17a, the evaporimeter 10 of foundation the 3rd embodiment is similar to the evaporimeter 10 among first embodiment.In the 3rd embodiment, with respect to air-flow direction A1, skew wall 17a tilts with respect to the plane of body portion 13, as shown in Figure 10.
For example, the downstream curved wall of each skew wall 17a and semi-cylindrical hill 14 tilts in the same direction.In other words, skew wall 17a tilts towards downstream position with respect to air-flow direction A1.Particularly, skew wall 17a forms tiltangle b with respect to the plane of body portion 13, so that the distance between the plane of skew wall 17a and body portion 13 upstream increases the position with respect to air-flow direction A1.
In this case, because the guiding effect of inclination and offset wall 17a, air-flow is directed along the downstream curved wall of projection 14.Therefore, be reduced, as by among Figure 10 shown in the arrow Q1 in of the separation of projection 14 downstream position air-flow from heat transfer plate 12 surfaces.Just, the minimizing of the heat transfer coefficient that causes owing to the separation of air-flow is lowered.Therefore, further improve heat transfer efficiency.Equally in this case, skew wall 17a can further be tilted with respect to above-below direction, to be similar to the mode of second embodiment.
(the 4th embodiment)
The evaporimeter 10 of foundation the 4th embodiment is similar to the evaporimeter 10 among the 3rd embodiment, and difference is to be offset wall 17a and has curved shape with the serpentine shape steering current along air duct 18.
As shown in Figure 11, skew wall 17a is curved inwardly, so that the distance between the plane of skew wall 17a and body portion 13 reduces to mid portion with respect to air-flow direction A1.Therefore, because the guiding effect of the curved shape of skew wall 17a, air-flow can be directed along the curved surface of projection 14, as by shown in the arrow A 2.Therefore, with respect to air-flow direction A1, in projection 14 upstream and downstream position, air-flow is unlikely from the surface isolation of heat transfer plate 12, as by shown in arrow Q1, the Q2.Therefore, than the 3rd embodiment,, the heat transfer coefficient that the separation of air-flow causes is further reduced because reducing.Therefore, further improved heat transfer efficiency.
(the 5th embodiment)
Except the shape of fin 17, the evaporimeter 10 of foundation the 5th embodiment is similar to the evaporimeter 10 among first embodiment.The shape of fin 17 is not limited to the shape of roughly U-shaped as shown in FIG. 5, but can change.
For example, fin 17 is formed with the smooth curved shape and protrudes, as shown in Figure 12.In this case, skew wall 17a is the curved wall that protrudes with the form of semicircle or half-oval shaped roughly from body portion 13.The two ends of curved wall are connected to body portion 13.Because the shape of fin 17 is level and smooth or soft, therefore be enhanced by protruding formation fin 17.
(the 6th embodiment)
Except following structure, the evaporimeter 10 of foundation the 6th embodiment is similar to the evaporimeter 10 among first embodiment.In first embodiment, first and second heat transfer plates 12 have fin 17.Selectively, in the 6th embodiment, in first and second heat transfer plates 12 only one have fin 17
For example, as shown in Figure 13, first heat transfer plate (left heat transfer plate) 12 has fin 17.Yet, form a pair of second heat transfer plate (right heat transfer plate) 12 in first heat transfer plate 12 and do not have fin 17.On the contrary, second heat transfer plate 17 forms hole 13a in the position corresponding to the fin 17 of first heat transfer plate 12.For example, hole 13a is formed by punching press.In addition in this case, fin 17 and hole 13a are set at a plurality of positions on the above-below direction.
In the example shown in Figure 13, with respect to above-below direction, hole 13a is positioned in the zone of hole 17d of fin 17.In other words, hole 17d and hole 13a are set to overlap at least between first and second heat transfer plates 12.
Like this, the inner space of the fin 17 of first heat transfer plate 12 is connected by hole 13a with the space outerpace of second heat transfer plate 12.Therefore, the condensed water of the inner space of fin 17 can be directed to the outside of heat transfer plate 12.Condensed water will further flow on downward direction, shown in arrow T.In other words, the discharge-channel that is used to discharge condensed water can be provided by the inner space of fin 17.Therefore, condensed water will be discharged effectively.
For example, the size G of the hole 17d of fin 17 is equal to or greater than in 5 the situation on above-below direction, and condensed water is further discharged effectively.The size K of hole 13a is equal to or greater than in the fin width Fw situation of fin 17 on above-below direction, and condensed water can be disposed to the outside of heat transfer plate 12 effectively by hole 13a.Therefore, further improved emission effect.Further, be equal to or greater than in the situation of fin width Fw of fin 17, further improved emission effect in size with respect to the hole 13a of air-flow direction A1.
(the 7th embodiment)
The evaporimeter 10 of foundation the 7th embodiment is similar to the evaporimeter 10 of the 6th embodiment, but the position of hole 13a and fin 17 is changed.
As shown in Figure 14, each hole 13a is positioned as the corresponding aperture 17d that is lower than fin 17 slightly.Particularly, with respect to above-below direction, the lower end 13b of each hole 13a is positioned as the lower end 17e that is lower than respective aperture 17d.
Because lower end 17e and the hole 17a of hole 17d are overlapping, so condensed water can be disposed to the outside of heat transfer plate 12 smoothly from the lower end 17e of fin 17 by hole 13a.Like this, condensed water will be discharged effectively.
In the example shown in Figure 14, with respect to above-below direction, the upper end 13c of hole 13a is positioned as the upper end 17f that is lower than hole 17d.Replacedly, the upper end 13c of hole 13a can be in the height place identical with hole 17d upper end 17f or be positioned as the upper end 17f that is higher than hole 17d.
(modification)
In the above embodiments, with respect to air-flow direction A1, projection 14 is positioned in the same position place of paired heat transfer plate 12.Replacedly, with respect to air-flow direction A1, projection 14 can be positioned in the diverse location of paired heat transfer plate 12.For example, with respect to air-flow direction A1, projection 14 can be arranged in the paired heat transfer plate 12 by interlace mode.
In the above among the embodiment, projection 14 extends upward at upper and lower, promptly on gravity direction.Here " above-below direction " and " gravity direction " should strictly not represent the direction of gravity, and can slight inclination.That is, the connotation of " above-below direction " and " gravity direction " comprises from the direction of the strict direction slight inclination of gravity.
In the above among the embodiment, projection 14 extends upward at upper and lower.Yet the longitudinal direction of projection 14 is not necessarily always corresponding to above-below direction.Projection 14 can be extended on the direction that intersects with air-flow direction A1.For example, with respect to above-below direction, projection 14 can obliquely be extended.
In second embodiment shown in Fig. 9, with respect to above-below direction, skew wall 17a tilts with respect to the plane of body portion 13.In the 3rd embodiment shown in Figure 10, with respect to air-flow direction A1, skew wall 17a tilts with respect to the plane of body portion 13.Replacedly, can dispose skew wall 17a by the structure that makes up the second and the 3rd embodiment.Just, skew wall 17a can be tilted with respect to above-below direction and air-flow direction A1.
In the 4th embodiment, skew wall 17a has curved shape, flows with the serpentine shape guiding air along air duct 18.Replacedly, skew wall 17a can have the shape that is made of the shape of shape among combination second embodiment and the 4th embodiment.
Among the embodiment, core component 11 and case slot space are formed by whole by piling up heat transfer plate 12 in the above.Replacedly, core component 11 can form by piling up heat transfer plate 12, and the case slot space can separate formation with core component 11.
In the above among the embodiment, two are separated heat transfer plate 12 and are matched and be connected to each other, and coolant channel 15,16 is formed on the inside of the projection 14 of heat transfer plate 12.Replacedly, heat transfer plate 112 can form in the base portion connection by folding single plate member and with folding plate in pairs, the projection that is used for coolant channel on described single plate member is formed two, is similar to the mode of the plate shown in Figure 36 of USP6401804 (Japanese laid-open patent open No.2001-41678).
In addition, in pairs heat transfer plate 12 can connect by attaching parts, is similar to the mode of structure shown in Figure 35 of USP6401804.
Among the embodiment, " 12 pairs of heat transfer plates " comprises that with " heat transfer plate 12 in pairs " two separating plates, 12 connected situations are folded and situation about being connected in the reservations office with spiral-plate in the above.
In the 6th and the 7th embodiment, fin 17 is formed on first heat transfer plate 12, and hole 13a is formed on second heat transfer plate 12.Yet fin 17a and hole 13a can be formed first and second heat transfer plates 12 on both.For example, fin 17 and hole 13a alternately are formed on first heat transfer plate 12 with embarking on journey, and fin 17 and hole 13a alternately are formed on second heat transfer plate 12 with embarking on journey.First and second heat transfer plates 12 are connected, so that the row of the hole 13a of corresponding second heat transfer plate 12 of row difference of the row of the fin 17 of first heat transfer plate 12 and hole 13a and the row of fin 17.Equally, in this case, had similar effect.
In the 6th and the 7th embodiment, fin 17 can have Any shape and the arrangement architecture the same with the fin 17 of first to the 5th embodiment.
Among the embodiment, as evaporimeter, in described evaporimeter, low pressure, low-temperature refrigerant in the cold-producing medium circulation flow through coolant channel 15 to heat exchanger 10 by exemplarily in the above.Yet the fluid that flows through coolant channel (internal fluid channels) is not limited to cold-producing medium, and can be any other cryogenic fluid, for example cooling water etc.Just, the heat exchanger above among the embodiment can be used as any cooling heat exchanger that is used for any purpose.
To those skilled in the art, can easily expect other advantage and change.Therefore, illustrated in relative broad range of the present invention is not limited to and described detail, represent device and illustrative example.
Claims (26)
1. heat exchanger, described heat exchanger are used for implementing heat exchange at the air of its flows outside with between the internal flow that portion flows within it, thereby the cooling air comprises:
First heat transfer plate; With
Second heat transfer plate, wherein
In first and second heat transfer plates each comprises body portion and a plurality of projection of qualification along the plane of air-flow direction, described a plurality of projection is protruded and is extended in the direction that intersects with air-flow direction from body portion, described projection is defined for the inner flow passage that allows fluid flow inside therein
First and second heat transfer plates are connected to each other, so that body portion contacts with each other, the projection of first heat transfer plate is projection in one direction, and the projection of second heat transfer plate is projection in the opposite direction,
In first and second heat transfer plates each further comprises fin part outstanding from body portion along the direction identical with projection and the hole corresponding to fin position partly on body portion,
Fin partly comprises the skew wall, and described skew wall is from the body portion skew and limit space in the fin therein,
Isolated two positions of skew wall on the direction of the longitudinal direction that is parallel to projection are connected to body portion, and
Longitudinal direction with respect to projection, the hole of first heat transfer plate is from the hole displacement of second heat transfer plate, the space is connected by described hole with the interior space of the fin of second heat transfer plate in the fin of first heat transfer plate, makes the communication passage that is provided for discharging condensed water between first and second heat transfer plates.
2. according to the heat exchanger of claim 1, wherein
On the direction perpendicular to the plane of body portion, fin partly has fin height, and described fin height is equal to or greater than 0.35mm.
3. according to the heat exchanger of claim 1, wherein
In first and second heat transfer plates each has a plurality of fin parts that comprise described fin part, described a plurality of fin partly is set on the flow direction of air, makes to comprise that a plurality of communication passage of described communication passage are set on the flow direction of air.
4. heat exchanger, described heat exchanger are used for implementing heat exchange at the air of its flows outside with between the internal flow that portion flows within it, thus the cooling air, and described heat exchanger comprises:
First heat transfer plate, it comprises body portion, a plurality of projectioies, the fin part and first hole, described body portion limits the plane along air-flow direction, described a plurality of projection is protruded and is extended in the direction that intersects with air-flow direction from body portion, described fin part is being protruded along the direction identical with projection from body portion and is being limited space in the fin therein, the position corresponding to fin part of described first hole on base wall, described fin comprises that partly from the skew wall of body portion skew, described skew wall is connected to body portion in two positions that the longitudinal direction along projection separates; With
Second heat transfer plate, it comprises body portion, a plurality of projection and second hole, and described body portion limits the plane along air-flow direction, and described a plurality of projectioies are protruded and are extended in the direction that intersects with air-flow direction from body portion, wherein
First heat transfer plate and second heat transfer plate are connected to each other, so that its body portion is in contact with one another, the projection of first heat transfer plate is protruded in one direction, and the projection of second heat transfer plate is protruded in the opposite direction, the projection of first and second heat transfer plates be defined for therein the inner flow passage that allows fluid flow inside and
Overlap at least in first hole and second hole.
5. according to the heat exchanger of claim 4, wherein
First heat transfer plate comprises a plurality of fin parts that comprise described fin part and a plurality of first holes that comprise described first hole, and described a plurality of fins partly are set on the longitudinal direction of projection, and described a plurality of first holes are set on the longitudinal direction of projection, and
Second heat transfer plate comprises a plurality of second holes that comprise described second hole, and described a plurality of second holes are set on the longitudinal direction of projection.
6. according to the heat exchanger of claim 4, wherein the size of second hole on the longitudinal direction of projection is equal to or greater than the width of fin part on air-flow direction.
7. according to the heat exchanger of claim 4, wherein second hole is equal to or greater than the width of fin part on air-flow direction in the size on the air-flow direction.
8. according to the heat exchanger of claim 4, wherein said second hole is provided so that its lower end is lower than the lower end in first hole.
9. according to the heat exchanger of claim 4, wherein
First heat transfer plate comprises a plurality of fin parts that comprise described fin part and a plurality of first holes that comprise described first hole, and described a plurality of fins partly are set on the flow direction of air, and described a plurality of first holes are set on the flow direction of air,
Second heat transfer plate comprises a plurality of second holes that comprise described second hole, and described a plurality of second holes are set on the flow direction of air, and
Overlap at least in a corresponding hole in each hole in described a plurality of first hole and described a plurality of second hole.
10. according to the heat exchanger of claim 3 or 9, wherein said a plurality of fin parts are spaced apart on the flow direction of air, and the distance between the two adjacent fins part is equal to or greater than 0.4mm.
11. according to each heat exchanger in the claim 1 to 9, wherein the size of each hole on the longitudinal direction of projection is equal to or greater than 5mm.
12., wherein be offset the plane that wall is parallel to described body portion according to each heat exchanger in the claim 1 to 9.
13., wherein be offset wall and tilt, so that the distance between the plane of skew wall and body portion reduces towards lower position with respect to the plane of described body portion according to each heat exchanger in the claim 1 to 9.
14. according to each heat exchanger in the claim 1 to 9, wherein
Each projection comprises curved exterior surface,
Fin partly is set at the downstream of one of projection with respect to air-flow direction,
The skew wall tilts with respect to the plane of body portion, so that the distance between the plane of skew wall and body portion reduces towards downstream position with respect to air-flow direction.
15. according to each heat exchanger in the claim 1 to 9, wherein
Each projection comprises curved exterior surface,
Fin partly is set between two projectioies, described two projectioies be set on the air-flow direction and
The skew wall is towards the plain bending of body portion, so that the distance between the plane of skew wall and body portion reduces towards the centre position with respect to air-flow direction.
16. according to each heat exchanger in the claim 1 to 9, wherein
Fin partly comprise will the skew wall the lower end that is connected to first connecting wall of body portion and will be offset wall, upper end be connected to second connecting wall of body portion.
17. according to the heat exchanger of claim 16, wherein
First connecting wall and second connecting wall tilt with respect to the plane of body portion respectively, and each the inclination angle in first connecting wall and second connecting wall is at least 30 degree with 60 spend at the most.
18. according to the heat exchanger of claim 16, wherein
Form between the skew upper end of wall and first connecting wall fillet and
Form fillet between the lower end of skew wall and second connecting wall.
19. according to each heat exchanger in the claim 1 to 9, wherein
The skew wall on the cross section that limits along protruding longitudinal direction, have semicircular in shape and
The end of skew wall is connected to body portion.
20. according to the heat exchanger of claim 1, wherein
The fin part has the width that is equal to or greater than 0.2mm with respect to air-flow direction.
21. according to the heat exchanger of claim 20, wherein
Body portion comprises with respect to the sidepiece of air-flow direction at fin part opposite side, and each described sidepiece is equal to or greater than 0.15mm with respect to the width of air-flow direction.
22. according to the heat exchanger of claim 21, wherein
The width of each described sidepiece is equal to or greater than 0.5mm.
23. according to each heat exchanger in the claim 1 to 9, wherein
The projection of the projection of first heat transfer plate and second heat transfer plate is set on the identical position with respect to air-flow direction, so that one of projection of one of the projection by first heat transfer plate and second heat transfer plate is provided with each internal fluid channels.
24., further comprise according to each heat exchanger in the claim 1 to 9:
A plurality of first heat transfer plates that comprise described first heat transfer plate; With
A plurality of second heat transfer plates that comprise described second heat transfer plate, wherein
Described a plurality of first heat transfer plate and described a plurality of second heat transfer plate be arranged in pairs and
First heat transfer plate and second heat transfer plate are to being stacked on the direction perpendicular to the plane of body portion, so that the gap that allows air to flow is set between the phase adjacency pair of first heat transfer plate and second heat transfer plate.
25. according to the heat exchanger of claim 24, wherein
The size in each gap of the position between the surface of the skew wall of a heat transfer plate and another heat transfer plate is equal to or greater than 0.15mm, and it is relative that described another heat transfer plate and a described heat transfer plate stride across described gap.
26. according to each heat exchanger in the claim 1 to 9, wherein
Fin part is set at the upstream of end-boss with respect to air-flow direction, and described end-boss is one of a plurality of projectioies and is positioned in downstream position in a plurality of projectioies with respect to air-flow direction.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006298691A JP2008116102A (en) | 2006-11-02 | 2006-11-02 | Heat exchanger for cooling |
| JP2006298691 | 2006-11-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101173841A true CN101173841A (en) | 2008-05-07 |
| CN100552360C CN100552360C (en) | 2009-10-21 |
Family
ID=39358754
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB200710167210XA Expired - Fee Related CN100552360C (en) | 2006-11-02 | 2007-11-01 | Cooling heat exchanger |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20080105416A1 (en) |
| JP (1) | JP2008116102A (en) |
| CN (1) | CN100552360C (en) |
| DE (1) | DE102007051194A1 (en) |
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2007
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- 2007-11-01 US US11/982,213 patent/US20080105416A1/en not_active Abandoned
- 2007-11-01 CN CNB200710167210XA patent/CN100552360C/en not_active Expired - Fee Related
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Also Published As
| Publication number | Publication date |
|---|---|
| DE102007051194A1 (en) | 2008-07-31 |
| JP2008116102A (en) | 2008-05-22 |
| US20080105416A1 (en) | 2008-05-08 |
| CN100552360C (en) | 2009-10-21 |
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Granted publication date: 20091021 Termination date: 20101101 |