CN104334994A - Plate-type heat exchanger and refrigeration cycle device comprising same - Google Patents
Plate-type heat exchanger and refrigeration cycle device comprising same Download PDFInfo
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- CN104334994A CN104334994A CN201380029412.1A CN201380029412A CN104334994A CN 104334994 A CN104334994 A CN 104334994A CN 201380029412 A CN201380029412 A CN 201380029412A CN 104334994 A CN104334994 A CN 104334994A
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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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
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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
- F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
- F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
- F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
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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
- F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
- F28F2265/16—Safety or protection arrangements; Arrangements for preventing malfunction for preventing leakage
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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
- F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
- F28F3/027—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements with openings, e.g. louvered corrugated fins; Assemblies of corrugated strips
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- 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 heat exchanger (1) that improves heat exchange efficiency, has a simple structure and can be inexpensively produced, is capable of improving long-term reliability of a device as a result of prevention of fluid leakage, and comprises: a plurality of heat transfer plates (5); a plurality of inner fins (9); and a plurality of leakage prevention plates (7). Passage holes through which fluid is fed are provided in the leakage prevention plates. The inner fins in a first flow path and the inner fins in a second flow path are provided such that the thermal resistivity ratio between the two fluids is the same.
Description
Technical field
The present invention relates to heat-exchangers of the plate type and possess its freezing cycle device.
Background technology
Stacked multiple heat transfer plate in heat-exchangers of the plate type, this heat transfer plate is formed with the concavo-convex of multiple row waveform.As heat-exchangers of the plate type in the past, the line proposing the summit (or the point at the end of paddy) at the peak being configured to the waveform linking heat transfer plate relative to adjacent heat transfer plate intersect chevron shaped.Further, also proposed compared with chevron shaped heat-exchangers of the plate type, the profile design of heat transfer plate is made to have the heat exchanger (such as, see patent document 1) of the inner fin type of the free degree.
Problem such below existing in chevron shaped heat-exchangers of the plate type.Chevron shaped heat-exchangers of the plate type due to heat transfer plate be waveform shape, so, between the 1st fluid (such as, cold-producing medium) and the 2nd fluid (such as, water), be difficult to form anti-leak function.Because the hot water generated by the heat-exchangers of the plate type being mounted in hot water supply device is used in bathing pool water, so, need cold-producing medium can not be leaked in this water.Thus, if there is no anti-leak function, then hot water supply device can not be used in as the combustible refrigerant that the CO2 of high-pressure refrigerant or hydrocarbon, low GWP cold-producing medium are such.In addition, because flow path cross sectional area is roughly equal, so when making the flowing of different fluid, both thermal resistance ratio is also unequal, and heat exchanger effectiveness is bad.Further, the junction surface of adjacent plate is formed by the point cantact of ripple, bonding area is little, easily bad.
In addition, also there is following such problem in the heat exchanger of the inner fin type that patent document 1 is such.First, the heat exchanger due to inner fin type does not have anti-leak function, so, be difficult to use in hot water supply device.The shape of inner fin is identical with regard to the 1st stream and the 2nd stream, and be not the optimum shape corresponding to the fluid of flowing, therefore, heat exchanger effectiveness is bad.In addition, inner fin becomes the specification needing intensity to match with the fluid of a side, and the fluid side of the opposing party becomes the inner fin with excessive bonding area, and therefore, cost uprises.
In addition, as other heat exchanger in the past, such as, patent document 2 discloses the structure of the 1st stream plate and the 2nd stream plate that possess and comprise stream in the wall thickness of respective plate and the demarcation strip separated by these stream plates.But in the structure that relevant patent document 2 is such, demarcation strip is simple plate-shaped member, can not be used in the form using inner fin.
In addition, as the heat exchanger possessing anticorrosion component, there is heat exchanger disclosed in patent document 3.But the disclosed subplate as anticorrosion component of patent document 3 is plane, only for the separation in the face of pipe peace, can not be used in the folded form of multiple flaggy.In addition, the heat exchanger of patent document 3 owing to being the fluid flowed in pipe and the fluid flowed between fin, so the contact surface by means of only pipe and central layer carries out heat exchange, therefore, heat exchanger effectiveness is lower than the heat exchanger of stacked multiple inner fin.
At first technical literature
Patent document
Patent document 1: Japanese Unexamined Patent Publication 2003-185375 publication (the 5th page, Fig. 1)
Patent document 2: Japanese Unexamined Patent Publication 2008-157544 publication (the 7th page, Fig. 2)
Patent document 3: Japanese Unexamined Patent Publication 2009-133506 publication (the 12nd page, Fig. 4)
Summary of the invention
The problem that invention will solve
The present invention is the invention made in view of the foregoing, its objective is and provides one to make heat exchanger effectiveness good, and simple structure, can manufacture at an easy rate, and the heat-exchangers of the plate type of the long-term reliability of the device brought by the leakage of anti-fluid can be improved.
For solving the means of problem
In order to realize above-mentioned object, heat-exchangers of the plate type of the present invention possesses: multiple heat transfer plate, has flat heat-transfer area respectively; With multiple inner fin, the 1st stream and the 2nd stream is alternately formed between every a pair previous heat transfer plate, aforementioned multiple inner fin is configured in corresponding aforementioned 1st stream or the 2nd stream respectively, wherein, it is different that the aforementioned inner fin being configured in aforementioned 1st stream and the aforementioned inner fin being configured in aforementioned 2nd stream are configured to heat transfer area, between a pair previous heat transfer plate, be configured with anti-leak plate, this anti-leak plate is formed with the via hole at least making aforementioned 1st fluid or the circulation of the 2nd fluid.
Invention effect
According to the present invention, make heat exchanger effectiveness good, and simple structure, can manufacture at an easy rate, and the long-term reliability of the device brought by the leakage of anti-fluid can be improved.
Accompanying drawing explanation
Fig. 1 is the exploded perspective view of the offset fin plate-type heat exchanger represented in embodiments of the present invention 1.
Fig. 2 is the stereogram of inner fin.
Fig. 3 is the stereogram representing the inner fin in the 1st stream and the inner fin in the 2nd stream from oblique upper.
Fig. 4 is the top view representing the inner fin in the 1st stream and the inner fin in the 2nd stream.
Fig. 5 is the figure of the feature that embodiments of the present invention 2 are described.
Detailed description of the invention
Below, with reference to the accompanying drawings, the embodiment of offset fin plate-type heat exchanger of the present invention is described.In addition, identical in figure Reference numeral represents identical or corresponding part.
Embodiment 1.
Fig. 1 is the exploded perspective view of the offset fin plate-type heat exchanger represented in embodiments of the present invention 1.In addition, Fig. 2 is the stereogram of inner fin.Fig. 3 is the stereogram representing the inner fin in the 1st stream and the inner fin in the 2nd stream from oblique upper, and Fig. 4 is the top view representing the inner fin in the 1st stream and the inner fin in the 2nd stream.Heat-exchangers of the plate type 1 possesses at least one pair of side plate 3, is configured in multi-disc heat transfer plate 5 between these side plates 3 and anti-leak plate 7 and at least one pair of inner fin 9 respectively.
Pair of side plates 3 plays the effect strengthened, respective four corners be provided with become the 1st fluid entrance 11, the outlet 13 of the 1st fluid, the entrance 15 of the 2nd fluid, the outlet 17 of the 2nd fluid four via holes.In addition, in illustrated example, see the entrance 11 of upper corner configuration the 1st fluid in side side, left and right one at Fig. 1, in the outlet 13 of lower corner configuration the 1st fluid, at the entrance 15 of lower corner configuration the 2nd fluid of the opposing party side, left and right, in the outlet 17 of upper corner configuration the 2nd fluid.In addition, in FIG, represent the flow direction of the 1st fluid with Reference numeral X, represent the flow direction of the 2nd fluid with Reference numeral Y.
The through hole as via hole is formed at four respective corners of heat transfer plate 5 and anti-leak plate 7.Specifically, as via hole on heat transfer plate 5, be provided with the 1st fluid outlet hole 11c, the 1st fluid return road hole 13c, the 2nd fluid outlet hole 15c and the 2nd fluid return road hole 17c.Equally, on anti-leak plate 7, via hole is provided with the 1st fluid outlet hole 11d, the 1st fluid return road hole 13d, the 2nd fluid outlet hole 15d and the 2nd fluid return road hole 17d.
Heat transfer plate 5 and anti-leak plate 7 are all, by punching press etc., the component processing of roughly uniform for wall thickness tabular is shaped as irregular plate.Heat transfer plate 5 is the parts with the flat heat-transfer area forming the 1st corresponding stream or the 2nd stream respectively.Heat transfer plate 5 each on be formed with recess 5a as relative relation and protuberance 5b.
As shown in Figure 1, if the heat transfer plate 5 of the 1st stream that the 1st fluid that formation represents for Reference numeral X passes, then recess 5a occupy the 1st fluid outlet hole 11c, the 1st fluid return road hole 13c and between which with the wide region faced by inner fin 9, protuberance 5b occupies peripheral part of the 2nd fluid outlet hole 15c and the 2nd fluid return road hole 17c.In addition, if the heat transfer plate 5 of the 2nd stream that the 2nd fluid that formation represents for Reference numeral Y passes, then recess 5a occupy the 2nd fluid outlet hole 15c, the 2nd fluid return road hole 17c and between which with the wide region faced by inner fin 9, protuberance 5b occupies peripheral part of the 1st fluid outlet hole 11c and the 1st fluid return road hole 13c.
Anti-leak plate 7 is the parts becoming the back side of inboard of the stream forming surface being configured in corresponding heat transfer plate 5 respectively.In addition, the region that anti-leak plate 7 matches at the heat-transfer area with heat transfer plate 5 respectively has flat part, and the recess 7a had as relative relation and protuberance 7b.As shown in Figure 1, the face respectively with the rough pattern of the form identical with the stream forming surface side on the surface as corresponding heat transfer plate 5 of anti-leak plate 7 is laminated in the inside of its corresponding heat transfer plate 5.Accordingly, corresponding heat transfer plate 5 and anti-leak plate 7 just in time match, to make the inside of heat transfer plate 5 consistent with the concave-convex surface of anti-leak plate 7.Like this, heat transfer plate 5 and anti-leak plate 7 roughly contact throughout integrally carrying out face, and heat transfer plate 5 and anti-leak plate 7 press together at wide area mutually.
Inner fin 9 is the offset fin for promoting heat transfer be configured between corresponding heat transfer plate 5 and anti-leak plate 7.Inner fin 9 is the form of the roughly tabular that width and short transverse are larger than thickness direction respectively, as shown in Figure 2, comprises following structure: shell element extends throughout width, with being concavo-convexly concatenated to form of being formed with making approximate right angle.In addition, these concavo-convex ends (top and bottom) is formed by level land, and inner fin 9 yet carries out face contact relative to the heat transfer plate 5 of correspondence, anti-leak plate 7 in flat end.
In addition, the inner fin 9 being configured in the 1st stream is different with the heat transfer area of the inner fin 9 being configured in the 2nd stream.Specifically, as shown in Figure 3 and 4, the inner fin 9 (9a) being configured in the 1st stream and the inner fin 9 (9b) being configured in the 2nd stream use the inner fin that size is mutually different.In illustrated example, the inner fin 9 (9b) being configured in the 2nd stream to be concavo-convexly made up of more tiny than the inner fin 9 (9a) being configured in the 1st stream.In addition, for the inner fin 9 in Fig. 1, pay the utmost attention to illustrated clearness, similarly depict the inner fin being configured in the 1st stream and the inner fin being configured in the 2nd stream.
Together with heat transfer plate 5 is brazed on the anti-leak plate 7 of correspondence respectively, further, together with the heat transfer plate 5 that tegillum builds up the correspondence clipping corresponding inner fin 9 is brazed on anti-leak plate 7.
As illustrated in Figure 1 like that, the inner fin 9 of the inner fin 9 of the inner fin 9 of side plate 3, anti-leak plate 7, the 1st stream, the heat transfer plate 5 of the 1st stream, the anti-leak plate 7 just in time matched with the heat transfer plate 5 of the 1st stream, the 2nd stream, the heat transfer plate 5 of the 2nd stream, the anti-leak plate 7 just in time matched with the heat transfer plate 5 of the 2nd stream, the 1st stream etc. and subsequently superimposed elements be as required iteratively processed configure, stacked, finally, the lit-par-lit structure having obtained side plate 3 stacked.
According to the heat-exchangers of the plate type of present embodiment 1 described above, following such advantage can be obtained.First, in the heat-exchangers of the plate type of present embodiment, because the inside at heat transfer plate is provided with anti-leak plate, so, such as, even if the heat transfer plate of the 1st stream be formed for the 1st fluid circulation is damaged because of corrosion, also due to the existence of its anti-leak plate behind, because being in the existence of the cored solder between heat transfer plate and anti-leak plate, and can prevent the 1st fluid from leaking to the 2nd stream.In addition, due to the existence of cored solder, can also expect to suppress corrosion to further develop.Accordingly, the long-term reliability of the heat exchanger brought by the leakage of anti-fluid can be improved.In addition, due to the double-walled structure unlike chevron shaped heat-exchangers of the plate type containing air layer, so the decline of heat exchange amount is few, the expansion also can seeking to use fluid and the raising of heat exchange performance of accompanying with it.
And; in order to obtain the effect of the heat transfer plate that anti-leak plate protection has been corroded like this, be only that the anti-leak plate of generally flat shape is sandwiched between the heat transfer plate of a pair generally flat shape, so; the manufacture of heat exchanger can not be made complicated, can manufacture at an easy rate.Further, mutually contact with each other on surface in the part in flat face due to heat transfer plate, anti-leak plate and inner fin, so these heat transfer plates, anti-leak plate and inner fin are laminated together, be easily maintained as overall face contact form.
In addition, owing to not comprising for the such air layer of the double-walled structure of chevron shaped platelet heat exchangers, so the decline of the heat exchange amount caused by the decline of heet transfer rate is also few.Chevron shaped platelet heat exchangers due to the 1st fluid roughly the same with the flow path cross sectional area of the 2nd fluid, so when carrying out the heat exchange of water and cold-producing medium, compared with water side, the thermal resistance of refrigerant side becomes large, and heat exchanger effectiveness is bad.
On the other hand, in present embodiment 1, owing to using the inner fin that size is different, so, the refrigerant side that the impact of the pressure loss is large uses the fin of the tiny size that heat trnasfer is good, water side uses heat trnasfer poor but the fin that the pressure loss is little, accordingly, the thermal resistance ratio of cold-producing medium and water can be made equal.Like this, owing to can correspondingly adjust the thermal resistance ratio of the 1st fluid and the 2nd fluid with the physical property of fluid of flowing, so, the heat exchanger that heat exchanger effectiveness is high can be provided.
Anti-leak plate, by being formed into the via hole of gateway of fluid on the direction vertical with flat heat-transfer area, going for multiple flaggy to fold and in the stream of water side and this two side of refrigerant side, uses the form of inner fin.Have again, anti-leak plate because with the via hole vertical direction of flat heat-transfer area with the gateway becoming fluid, so, there is no need to form distribution configuration separately outside plate, can with by the stacked of plate, stream is formed thin such effect cooperatively makes heat exchanger more compactly.In addition, anti-leak plate because have the via hole of the gateway becoming fluid on the direction vertical with flat heat-transfer area, so, as mentioned above, in the 1st fluid and the 2nd fluid fluid diverse situation under, the diameter of via hole and the characteristic of fluid can be made to make matchingly.
If make aperture little, then can improve the flow velocity in via hole, when using as condenser, by making the aperture of steam side large, the increase of the pressure loss is reduced, make aperture little in liquid pipe side, make the discharge opeing of automatic heat-exchanger good, heat exchanger can be used well in the two-phase area efficiency of the good steam of heat trnasfer and liquid thus.
In addition, when heat exchanger be stacked 100,200 such multiple plates and there is the structure of a lot of stream, by adjusting the footpath of via hole, distribute to each stream equalization, but, if guaranteed the present embodiment of via hole by anti-leak plate and heat transfer plate, owing to easily can be made by punching press, so, local adjusting hole footpath can not be increased into.
In addition, as the advantage can carrying out the adjustment in aperture simply, can realize by making the little flow velocity improving fluid in aperture simply, fluid is flowed in a large number from the inflow pipe of fluid to the stream of depth side, or, by making aperture large, fluid is flowed in a large number to the stream near inflow pipe.In addition, if owing to making aperture large, then flow velocity can be made little, so, the corrosion (erosion) caused because of flow velocity in via hole can be suppressed.
In addition, due to alternately stacked 1st stream and the 2nd stream, between these streams, insert inner fin, so, each of 1st stream and the 2nd stream has following advantage: the face adjacent with inner fin is more than the structure of aforesaid patent document 2, and temperature efficiency is high.
Because the elongation of via hole and material has nothing to do, the diameter by means of only mould during punching press decides, so, the aperture of via hole can be made large, therefore, it is possible to suppress the pressure loss in via hole to increase, suppress the corrosion of accompanying with the high speed of fluid.
The flat heat-transfer area of inner fin and corresponding plate engages at face place each other.Thus, be the fluid that pressure is high at the 1st fluid, when 2nd fluid is pressure low fluid, by using the inner fin large with the contact area of plate for the 1st stream of the 1st fluid flowing, the 2nd stream for the 2nd fluid flowing uses the inner fin little with the contact area of plate, various piece is obtained to the enough intensity needed, the overall heat exchanger that can realize guaranteeing intensity without waste can be obtained.
As explained above, according to the present embodiment 1, equally heat exchanger effectiveness can be kept well by being remained by thermal resistance ratio between two fluids carrying out heat exchange, and, simple structure, can manufacture at an easy rate, and the long-term reliability of the device brought by the leakage of anti-fluid can be improved.Accordingly, the natural refrigerants such as non-serviceable CO2, flammable hydrocarbon, low GWP cold-producing medium because of not anti-refrigrant leakage function so far can be used.In addition, owing to using the selected scope of fluid to increase, so, the cold-producing medium that latent heat is large can be selected, can also heat exchange performance be improved.
Embodiment 2.
Then, according to Fig. 5, the heat-exchangers of the plate type of embodiments of the present invention 2 is described.In above-mentioned embodiment 1, as shown in Fig. 5 (a), employ and cover the overall such anti-leak plate 7 of heat transfer plate 5, but, in present embodiment 2, use the anti-leak plate 107 only covering the 1st fluid region adjacent with the 2nd fluid.That is, such as, as the form of anti-leak plate 107, as shown in Fig. 5 (b), can list and the periphery (protuberance 7b) of the 1st fluid outlet hole 11d in the anti-leak plate 7 of embodiment 1 is excised such form.Accordingly, the materials'use amount of anti-leak plate can be reduced, heat exchanger can be manufactured at an easy rate.
Embodiment 3.
As embodiments of the present invention 3, list the form being formed anti-leak plate 7,107 by clad material.If form anti-leak plate by clad material like this, then can enhance productivity.In manufacturing process, if sandwich cored solder by monomer, then there is the situation of cored solder from appropriate configured offset, become and engage bad reason.When forming heat exchanger, if laminated member increases, then speed of production slows down.But, due to the covering by anti-leak plate, these problems can be improved, so, the bad processing charges with reducing heat exchanger of soldering can be improved.
Embodiment 4.
As embodiments of the present invention 4, enumerate by the form of soldering by heat transfer plate, inner fin, anti-leak plate integration.By by constituent part soldered joint, the close property of each part can be improved, although to exist premised on anti-leak plate, it is possible to the decline suppressing heet transfer rate.If especially use the cored solder that the pyroconductivities such as copper are high, then the effect suppressing heet transfer rate to decline is large.Soldering due to the close property of each part good, so, the heat exchanger making bond strength high, stable create possibility.
Embodiment 5.
As embodiments of the present invention 5, the thickness of slab enumerating send as an envoy to heat transfer plate and anti-leak plate is the form of different size.If make the thickness ratio heat transfer plate of anti-leak plate large, then preventing the progress of the corrosion of heat exchanger, improve in intensity effective.If make the thickness ratio heat transfer plate of anti-leak plate little, then can reduce the thermal resistance of anti-leak plate, therefore, it is possible to suppress the decline of heat exchange performance, can also fee of material be reduced.Like this, if the thickness of slab of anti-leak plate and desired matching criteria select.
Embodiment 6.
As embodiments of the present invention 6, enumerate the freezing cycle device of the heat-exchangers of the plate type of any one of having carried in above-mentioned embodiment 1 ~ 5.Present embodiment 6, in the freezing cycle device being linked compressor, condenser (comprising gas cooler), expansion valve and evaporimeter by refrigerant piping successively, uses the heat-exchangers of the plate type of any one in embodiment 1 ~ 5 at both condenser and evaporimeter or any one party.According to the present embodiment 6, the freezing cycle device that reliability is high can be obtained.
Above see preferred embodiment, specifically understand content of the present invention, but according to basic technological thought of the present invention and enlightenment, various deformation form can be taked apparent to those skilled in the art.
Such as, anti-leak plate is for the situation of 1, but, also can overlapping multi-disc or formed by different materials.The material of the constituent part of heat exchanger also can use metal or the synthetic resin such as stainless steel, copper, aluminium, titanium.
In addition, as practical application of the present invention example, can be used in air-conditioning, generating, food pasteurization treatment facility etc. carried a lot of industry, the housed device of heat-exchangers of the plate type.
Description of reference numerals
1: heat-exchangers of the plate type; 5: heat transfer plate; 7: anti-leak plate; 9: inner fin.
Claims (7)
1. a heat-exchangers of the plate type, described heat-exchangers of the plate type possesses:
Multiple heat transfer plate, has flat heat-transfer area respectively; With
Multiple inner fin, alternately forms the 1st stream and the 2nd stream between every a pair previous heat transfer plate, and aforementioned multiple inner fin is configured in corresponding aforementioned 1st stream or the 2nd stream respectively,
It is characterized in that,
It is different that the aforementioned inner fin being configured in aforementioned 1st stream and the aforementioned inner fin being configured in aforementioned 2nd stream are configured to heat transfer area,
Between a pair previous heat transfer plate, be configured with anti-leak plate, this anti-leak plate is formed with the via hole at least making the 1st fluid or the circulation of the 2nd fluid.
2. heat-exchangers of the plate type as claimed in claim 1, is characterized in that,
The region that aforementioned anti-leak plate matches at the heat-transfer area with previous heat transfer plate respectively has flat part, and previous heat transfer plate and the mutual face of aforementioned anti-leak plate press together contiguously.
3. heat-exchangers of the plate type as claimed in claim 2, is characterized in that,
Aforementioned inner fin comprises the concavo-convex structure be concatenated to form, and aforementioned concavo-convex end is formed by level land, and this inner fin, relative to the heat transfer plate of correspondence and anti-leak plate, carries out face contact in flat aforesaid end.
4. the heat-exchangers of the plate type as described in any one in claims 1 to 3, is characterized in that,
Aforementioned anti-leak plate is configured to only cover the aforementioned 1st fluid region adjacent with aforementioned 2nd fluid respectively.
5. the heat-exchangers of the plate type as described in any one in Claims 1-4, is characterized in that,
Aforementioned anti-leak plate is formed by clad material respectively.
6. the heat-exchangers of the plate type as described in any one in claim 1 to 5, is characterized in that,
Make the thickness of slab of previous heat transfer plate and aforementioned anti-leak plate mutually different.
7. a freezing cycle device, is characterized in that,
At both condenser and evaporimeter or possess in claim 1 to 6 described in any one heat-exchangers of the plate type in any one party.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JPPCT/JP2012/064447 | 2012-06-05 | ||
| PCT/JP2012/064447 WO2013183113A1 (en) | 2012-06-05 | 2012-06-05 | Plate-type heat exchanger and refrigeration cycle device comprising same |
| PCT/JP2013/065456 WO2013183629A1 (en) | 2012-06-05 | 2013-06-04 | Plate-type heat exchanger and refrigeration cycle device comprising same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104334994A true CN104334994A (en) | 2015-02-04 |
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ID=49711534
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380029412.1A Pending CN104334994A (en) | 2012-06-05 | 2013-06-04 | Plate-type heat exchanger and refrigeration cycle device comprising same |
| CN201320320010.4U Expired - Lifetime CN203561252U (en) | 2012-06-05 | 2013-06-05 | Plate heat exchanger and refrigeration circulating device comprising same |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320320010.4U Expired - Lifetime CN203561252U (en) | 2012-06-05 | 2013-06-05 | Plate heat exchanger and refrigeration circulating device comprising same |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20150083379A1 (en) |
| EP (1) | EP2878909B1 (en) |
| CN (2) | CN104334994A (en) |
| WO (2) | WO2013183113A1 (en) |
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| CN111837010A (en) * | 2018-03-15 | 2020-10-27 | 三菱电机株式会社 | Plate heat exchanger, heat pump device provided with plate heat exchanger, and heat pump type cooling/heating/hot water supply system provided with heat pump device |
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| JP6091601B2 (en) * | 2013-03-22 | 2017-03-08 | 三菱電機株式会社 | Plate heat exchanger and refrigeration cycle apparatus equipped with the same |
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| DE102014217503A1 (en) | 2014-09-02 | 2016-03-03 | Illinois Tool Works Inc. | Dishwasher with a liquid transport line |
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| JP6007275B2 (en) * | 2015-03-20 | 2016-10-12 | 株式会社Ihi | Condenser and cleaning device |
| US20160377350A1 (en) * | 2015-06-29 | 2016-12-29 | Honeywell International Inc. | Optimized plate fin heat exchanger for improved compliance to improve thermal life |
| JP2017146068A (en) * | 2016-02-19 | 2017-08-24 | 三菱重工業株式会社 | Refrigerating machine and its control method |
| DE112019001350B4 (en) * | 2018-03-15 | 2024-06-13 | Mitsubishi Electric Corporation | Plate heat exchanger and heat pump device containing it |
| WO2020245876A1 (en) * | 2019-06-03 | 2020-12-10 | 三菱電機株式会社 | Plate-type heat exchanger, and heat transfer device |
| CN115210522A (en) * | 2020-03-05 | 2022-10-18 | 翰昂汽车零部件有限公司 | Plate heat exchanger |
| JP7301224B2 (en) * | 2020-05-19 | 2023-06-30 | 三菱電機株式会社 | Plate heat exchangers, refrigeration cycle equipment and heat transfer equipment |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5931219A (en) * | 1995-03-31 | 1999-08-03 | Behr Gmbh & Co. | Plate heat exchanger |
| JP2001099590A (en) * | 1999-09-30 | 2001-04-13 | Hisaka Works Ltd | Plate type heat exchanger |
| JP2001099585A (en) * | 1999-09-30 | 2001-04-13 | Denso Corp | Heat exchanger made of aluminum |
| JP2002107089A (en) * | 2000-09-29 | 2002-04-10 | Hisaka Works Ltd | Plate-type heat exchanger |
| JP2002203586A (en) * | 2000-12-28 | 2002-07-19 | Calsonic Kansei Corp | Heat exchanger for fuel cell |
| JP2003185375A (en) * | 2001-12-17 | 2003-07-03 | Daikin Ind Ltd | Plate-type heat exchanger |
| WO2008023732A1 (en) * | 2006-08-23 | 2008-02-28 | Tokyo Braze Co., Ltd. | Highly pressure-resistant compact heat exchanger, container for occluding hydrogen, and method of producing them |
| JP2010127554A (en) * | 2008-11-28 | 2010-06-10 | Hisaka Works Ltd | Heat exchanger plate unit and method of manufacturing plate type heat exchanger |
| US20110120678A1 (en) * | 2009-11-12 | 2011-05-26 | Autokuhler Gmbh & Co. Kg | Heat exchanger network |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2823139B2 (en) * | 1990-07-30 | 1998-11-11 | カルソニック株式会社 | Core part of housingless oil cooler |
| US5136854A (en) * | 1991-01-25 | 1992-08-11 | Abdelmalek Fawzy T | Centrifugal gas compressor - expander for refrigeration |
| SE9502135D0 (en) * | 1995-06-13 | 1995-06-13 | Tetra Laval Holdings & Finance | plate heat exchangers |
| JP3629900B2 (en) * | 1997-07-04 | 2005-03-16 | 株式会社デンソー | Heat exchanger |
| JP2002062078A (en) * | 2000-08-10 | 2002-02-28 | Sanyo Electric Co Ltd | Plate type heat exchanger |
| FR2845153B1 (en) * | 2002-10-01 | 2005-11-18 | Nordon Cryogenie Snc | WING FOR PLATE HEAT EXCHANGER, METHODS OF MANUFACTURING SUCH FIN, AND HEAT EXCHANGER COMPRISING SUCH AILET |
| US7506683B2 (en) * | 2004-05-21 | 2009-03-24 | Valeo, Inc. | Multi-type fins for multi-exchangers |
| US7618598B2 (en) * | 2004-11-29 | 2009-11-17 | Modine Manufacturing Company | Catalytic reactor/heat exchanger |
| JP2008157544A (en) | 2006-12-25 | 2008-07-10 | Mitsubishi Electric Corp | Heat exchanger and water heater |
| JP2009133506A (en) | 2007-11-28 | 2009-06-18 | Denso Corp | Heat exchanger and heat pump type water heater |
| WO2011117988A1 (en) * | 2010-03-25 | 2011-09-29 | 三菱電機株式会社 | Plate heat exchanger, plate heat exchanger producing method, and heat pump apparatus |
-
2012
- 2012-06-05 WO PCT/JP2012/064447 patent/WO2013183113A1/en active Application Filing
-
2013
- 2013-06-04 CN CN201380029412.1A patent/CN104334994A/en active Pending
- 2013-06-04 EP EP13800756.2A patent/EP2878909B1/en active Active
- 2013-06-04 US US14/398,310 patent/US20150083379A1/en not_active Abandoned
- 2013-06-04 WO PCT/JP2013/065456 patent/WO2013183629A1/en active Application Filing
- 2013-06-05 CN CN201320320010.4U patent/CN203561252U/en not_active Expired - Lifetime
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5931219A (en) * | 1995-03-31 | 1999-08-03 | Behr Gmbh & Co. | Plate heat exchanger |
| JP2001099590A (en) * | 1999-09-30 | 2001-04-13 | Hisaka Works Ltd | Plate type heat exchanger |
| JP2001099585A (en) * | 1999-09-30 | 2001-04-13 | Denso Corp | Heat exchanger made of aluminum |
| JP2002107089A (en) * | 2000-09-29 | 2002-04-10 | Hisaka Works Ltd | Plate-type heat exchanger |
| JP2002203586A (en) * | 2000-12-28 | 2002-07-19 | Calsonic Kansei Corp | Heat exchanger for fuel cell |
| JP2003185375A (en) * | 2001-12-17 | 2003-07-03 | Daikin Ind Ltd | Plate-type heat exchanger |
| WO2008023732A1 (en) * | 2006-08-23 | 2008-02-28 | Tokyo Braze Co., Ltd. | Highly pressure-resistant compact heat exchanger, container for occluding hydrogen, and method of producing them |
| JP2010127554A (en) * | 2008-11-28 | 2010-06-10 | Hisaka Works Ltd | Heat exchanger plate unit and method of manufacturing plate type heat exchanger |
| US20110120678A1 (en) * | 2009-11-12 | 2011-05-26 | Autokuhler Gmbh & Co. Kg | Heat exchanger network |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111819415A (en) * | 2018-03-15 | 2020-10-23 | 三菱电机株式会社 | Plate heat exchanger, heat pump device provided with plate heat exchanger, and heat pump type cooling/heating/water heating system provided with heat pump device |
| CN111837010A (en) * | 2018-03-15 | 2020-10-27 | 三菱电机株式会社 | Plate heat exchanger, heat pump device provided with plate heat exchanger, and heat pump type cooling/heating/hot water supply system provided with heat pump device |
| CN111819415B (en) * | 2018-03-15 | 2022-09-27 | 三菱电机株式会社 | Plate heat exchanger, heat pump device provided with same, and heat pump type cooling/heating/water heating system provided with heat pump device |
| US11662152B2 (en) | 2018-03-15 | 2023-05-30 | Mitsubishi Electric Corporation | Plate heat exchanger, heat pump device including plate heat exchanger, and heat pump cooling, heating, and hot water supply system including heat pump device |
| US11719495B2 (en) | 2018-03-15 | 2023-08-08 | Mitsubishi Electric Corporation | Plate heat exchanger, heat pump device including plate heat exchanger, and heat pump type of cooling, heating, and hot water supply system including heat pump device |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2013183629A1 (en) | 2013-12-12 |
| EP2878909A1 (en) | 2015-06-03 |
| WO2013183113A1 (en) | 2013-12-12 |
| CN203561252U (en) | 2014-04-23 |
| US20150083379A1 (en) | 2015-03-26 |
| EP2878909A4 (en) | 2016-04-27 |
| EP2878909B1 (en) | 2021-01-06 |
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Application publication date: 20150204 |