CN104380027A - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- CN104380027A CN104380027A CN201380032095.9A CN201380032095A CN104380027A CN 104380027 A CN104380027 A CN 104380027A CN 201380032095 A CN201380032095 A CN 201380032095A CN 104380027 A CN104380027 A CN 104380027A
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- Prior art keywords
- fluid
- road
- stream
- heat exchanger
- distribution
- Prior art date
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- 239000012530 fluid Substances 0.000 claims abstract description 80
- 230000015572 biosynthetic process Effects 0.000 abstract description 5
- 238000005192 partition Methods 0.000 abstract 2
- 230000002093 peripheral effect Effects 0.000 abstract 1
- 239000007788 liquid Substances 0.000 description 17
- 239000012071 phase Substances 0.000 description 7
- 230000008676 import Effects 0.000 description 4
- 239000003507 refrigerant Substances 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 239000007791 liquid phase Substances 0.000 description 3
- 230000002787 reinforcement Effects 0.000 description 3
- 238000000926 separation method Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 239000012141 concentrate Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
Classifications
-
- 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
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
- F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
-
- 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
- F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
-
- 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
-
- 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
- F28F3/042—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 in the form of local deformations of the element
- F28F3/046—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 in the form of local deformations of the element the deformations being linear, e.g. corrugations
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
Provided is a heat exchanger that is capable of evenly distributing fluid to a plurality of flow paths across a wide range of fluid flow rate states. The heat exchanger comprises a flow path formation section (51) having a plurality of aligned fluid flow paths; a distribution path formation section (53) having a distribution path (57) to which each of the entry ports (55) for the plurality of fluid flow paths is connected; and a cylindrical partition wall (59) that is provided inside the distribution path formation section, that has the distribution path positioned on the outside of the outer peripheral side thereof, and that demarcates an introduction path (63) on the inner side thereof. The cylindrical partition wall has a plurality of distribution holes (65), and when the flow path cross-sectional area of the introduction path is represented by S, the flow path diameter of the introduction path is represented by d, the sum total of the areas (sigma) of the plurality of distribution holes is represented by Sigmasigma, the alignment length of the plurality of distribution holes is represented by L, and the diameter of the distribution holes is represented by d', the following is satisfied: L/d' * pi(d/2)^2> Sigmasigma>= 2S.
Description
Technical field
The present invention relates to heat exchanger.
Background technology
In plate type heat exchanger, the concavo-convex heat transfer plate being formed with multiple row waveform, by multiple stacked, alternately forms the 1st stream and the 2nd stream between every a pair heat transfer plate.And, carry out heat exchange between the 1st fluid circulated in the 1st stream and the 2nd fluid circulated in the 2nd stream.
In addition, in plate type heat exchanger disclosed in patent document 1, the distributing pipe with a large amount of dispensing orifice is set in the lower space of the inlet side communication with multiple refrigerant flow path, the distribution of the equalization of plan cold-producing medium.
Prior art document
Patent document
Patent document 1: No. 8-504027, Japanese Kohyo
Summary of the invention
The problem that invention will solve
But, by means of only arranging the distributing pipe with dispensing orifice in the lower space of the inlet side communication with multiple refrigerant flow path, in refrigerant flow widely mode, the equalization distribution realizing cold-producing medium is difficult, especially, when cold-producing medium is low discharge, the possibility that the equalization that can not realize cold-producing medium is distributed is high.When heat exchanger plays function as evaporimeter, the cold-producing medium of gas-liquid two-phase state flows into distributing pipe, but in the flowing that flow is larger, the cold-producing medium of gas phase flows near tubular axis, there is the cold-producing medium of liquid phase around it with the gas-liquid separation state of the such radial direction of annular flow.On the other hand, in the flowing that the less flowing of the flow of cold-producing medium, flow velocity are little, caused by inertia force, the cold-producing medium of a large amount of liquid phases easily flow to the inboard of distributing pipe, and, there is the cold-producing medium of liquid phase in the downside of distributing pipe in a large number, there is the cold-producing medium of gas phase in upside in a large number, the gas-liquid separation state of such above-below direction occurs.Therefore, in the flowing that flow is less, cold-producing medium is flowed out equably from multiple dispensing orifice towards the bearing of trend of distributing pipe and becomes difficulty.Like this, in the flowing of high flow capacity and the flowing of low discharge, gas-liquid separation state is different, and especially, in the flow of refrigerant of low discharge, it is difficult for cold-producing medium being assigned to equably multiple stream.
The present invention makes in view of the foregoing, its objective is and provides a kind of heat exchanger, widely in mode, especially, in the flowing of low discharge, also heat exchange fluid can be assigned to multiple stream equably at the flow of heat exchange fluid.
For the technical scheme of technical solution problem
To achieve these goals, heat exchanger of the present invention has: stream forming portion, distribution road forming portion and cylindrical bulkhead, and described stream forming portion has the fluid flowing path of multiple arrangement, the distribution road that the respective entrance that described distribution road forming portion has described multiple fluid flowing path is communicated with, described cylindrical bulkhead is arranged in the forming portion of described distribution road, described distribution road is positioned at outside the periphery of described cylindrical bulkhead, and mark off in the inner side of described cylindrical bulkhead and import road, described cylindrical bulkhead has the multiple dispensing orifices being communicated with described importing road and described distribution road respectively, the flow path cross sectional area on described importing road is being set to S, the flow diameter on described importing road is set to d, the summation of the area σ of described multiple dispensing orifice is set to Σ σ, the spread length of described multiple dispensing orifice is set to L, when the diameter of described dispensing orifice is set to d ', L/d ' × π (d/2) ^2 > Σ σ >=2S.
The effect of invention
According to the present invention, widely in mode, especially, in the flowing of low discharge, also heat exchange fluid can be assigned to multiple stream equably at the flow of heat exchange fluid.
Accompanying drawing explanation
Fig. 1 is the stereogram of the inscape of the plate type heat exchanger representing embodiments of the present invention.
Fig. 2 is the figure representing plate type heat exchanger from side.
Fig. 3 is the figure of the plate of the main composition key element represented as plate type heat exchanger.
Fig. 4 is the figure of the neighbouring part of entrance of the 1st fluid representing plate type heat exchanger.
Fig. 5 is the sectional view of the V-V line along Fig. 4.
Fig. 6 is the stereogram relevant to cylindrical bulkhead.
Fig. 7 is the sectional view of the VII-VII line along Fig. 6.
Fig. 8 is the line chart of the relation represented between Σ σ/S and apportionment ratio D.
Fig. 9 represents the relation about between Σ σ/S and apportionment ratio D, the line chart of the difference produced by the direction of dispensing orifice.
Detailed description of the invention
Below, to the embodiment of heat exchanger of the present invention, be described based on accompanying drawing.In addition, in the drawings, same Reference numeral represents same or corresponding part.
Fig. 1 is the stereogram of the inscape of the plate type heat exchanger representing present embodiment, and Fig. 2 is the figure representing plate type heat exchanger from side.In addition, Fig. 3 is the figure of the plate of the main composition key element represented as plate type heat exchanger.
Plate type heat exchanger 1 has front side reinforcement side plate 3, rear side reinforcement side plate 5, be layered between these reinforcement side plates on front side of multiple heat transfer plate 7 respectively and heat transfer plate 9 on rear side of multiple.
In the corner of front side heat transfer plate 7, be provided with these four openings of outlet 17 of the entrance 11 of the 1st fluid, the outlet 13 of the 1st fluid, the entrance 15 of the 2nd fluid and the 2nd fluid.In addition, in the respective corner of front side heat transfer plate 7 and rear side heat transfer plate 9, these four through holes of Fu Lu hole 25 of the Fu Lu hole 21 of hole, past road the 19, the 1st fluid of the 1st fluid, hole, past road the 23, the 2nd fluid of the 2nd fluid are provided with.
In the present embodiment, be the example used using plate type heat exchanger 1 as evaporimeter, using cold-producing medium as the 1st fluid, and using water as the 2nd cold-producing medium.Specifically, as shown in Figure 1, cold-producing medium shown in arrow A flows in plate type heat exchanger 1 from the entrance 11 of the 1st fluid, is flowed, and flow out to plate type heat exchanger 1 from the outlet 13 of the 1st fluid by the hole, past road 19 of multiple 1st fluid and the Fu Lu hole 21 of multiple 1st fluid.In addition, the water shown in arrow B flows in plate type heat exchanger 1 from the entrance 15 of the 2nd fluid, is flowed, and flow out to plate type heat exchanger 1 from the outlet 17 of the 2nd fluid by the hole, past road 23 of multiple 2nd fluid and the Fu Lu hole 25 of multiple 2nd fluid.
In addition, the 1st stream and the 2nd stream is alternately formed between side heat transfer plate 7 and rear side heat transfer plate 9 in each of front.Thus, as the cold-producing medium of the 1st fluid when comprising the flowing in the lower space in hole, road 19 of multiple 1st fluid (closely, flow out from a large amount of dispensing orifice of distributing pipe as described below), and be assigned with and be supplied to multiple 1st stream, as indicated by arrow a 1, after moving up circuitously, concentrate on the upper space in the Fu Lu hole 21 comprising multiple 1st fluid, and flow out from the outlet 13 of the 1st fluid.Similarly, as the water of the 2nd fluid when comprising the flowing in the lower space in hole, road 23 of multiple 2nd fluid, be assigned with and be supplied to multiple 2nd stream, as shown in arrow B 1, after moving up circuitously, concentrate on the upper space in the Fu Lu hole 25 comprising multiple 2nd fluid, and flow out from the outlet 17 of the 2nd fluid.
Move up as shown in arrow A 1 and B1 period at the cold-producing medium as the 1st fluid and the water as the 2nd fluid, carry out heat exchange via across the front side heat transfer plate 7 of both correspondences and rear side heat transfer plate 9.Front side heat transfer plate 7 and rear side heat transfer plate 9 form multiple row waveform shape concavo-convex respectively, by these concavo-convex 27 formation the 1st stream and the 2nd streams.
Heat exchanger of the present invention has stream forming portion, distributes road forming portion and cylindrical bulkhead, is described them.Fig. 4 is the figure of the neighbouring part of entrance of the 1st fluid representing above-mentioned plate type heat exchanger, and Fig. 5 is the sectional view of the V-V line along Fig. 4.In addition, the definition of Fig. 5 priority declaration also schematically represents structure.And Fig. 6 is the stereogram relevant to cylindrical bulkhead, Fig. 7 is the sectional view of the VII-VII line along Fig. 6.
Stream forming portion 51 is parts of the fluid flowing path with multiple arrangement.The part upwards flowed with the fluid in above-mentioned front side heat transfer plate 7 and rear side heat transfer plate 9 plays function as stream forming portion 51.That is, as the fluid flowing path of multiple arrangement, multiple 1st stream along the stacked direction arrangement of front side heat transfer plate 7 and rear side heat transfer plate 9 and multiple 2nd streams of similarly arranging in the stacking direction are equivalent to.
Distributing road forming portion 53 is the parts with the distribution road 57 be communicated with each entrance 55 of multiple fluid flowing path.The part of the lateral flow (flowing by the hole, past road 23 of hole, past road the 19, the 2nd fluid of the 1st fluid) of the fluid in front side heat transfer plate 7 and rear side heat transfer plate 9 plays function as distributing road forming portion 53.
Cylindrical bulkhead 59 is arranged on distributes in road forming portion 53, in the concrete example of present embodiment, is the distributing pipe 61 toward the cylindrical shape in hole, road 23 toward hole, road 19 or multiple 2nd fluid interted at multiple 1st fluid.Distribute road 57 and be formed as ring-type outside the periphery of distributing pipe 61.In addition, in the inner side of distributing pipe 61, there is the importing road 63 marked off by the inner surface of distributing pipe 61.
Distributing pipe 61 is provided with multiple dispensing orifice 65.Multiple dispensing orifice 65 is communicated with importing road 63 respectively and distributes road 57.Multiple dispensing orifice 65 is along the bearing of trend of distributing pipe 61, that is, the stacked direction of front side heat transfer plate 7 and rear side heat transfer plate 9 is arranged side by side.
In the present embodiment, as shown in FIG. 6 and 7, multiple dispensing orifice 65 is all circular through hole, is formed as the size of same degree.In addition, multiple dispensing orifice 65 is to configure at equal intervals.In addition, as shown in Figure 5, the respective orientation size h of fluid flowing path is configured to identical size.
Mainly as shown in Figure 5, each entrance 55 of multiple fluid flowing path, above cylindrical bulkhead 59, is communicated with distribution road 57.In addition, as shown in Figure 7, more than 60% in multiple dispensing orifice 65 is formed facing downward in cylindrical bulkhead 59.That is, from distributing pipe 61, when each of multiple fluid flowing path upper side existing for entrance 55 is 0 degree, multiple dispensing orifice 65 is formed in the position of 180 degree of the lower side of the opposition side becoming entrance 55.
The diameter d of multiple dispensing orifice 65 ' be configured to 40 ~ 100% of the orientation size h of fluid flowing path respectively.In addition, by import road 63 flow path cross sectional area (using the orientation of fluid flowing path as vertical line such towards cross section) be set to S, the flow diameter importing road 63 is set to d, the summation of the area σ of multiple dispensing orifice 65 is set to Σ σ, the spread length (length between the edge, downstream of the upstream side edge of the dispensing orifice of side, most upstream and the dispensing orifice of most downstream side) of multiple dispensing orifice 65 is set to L, when the diameter of dispensing orifice 65 is set to d ', each pass pastern is formed in the mode meeting L/d ' × π (d/2) ^2 > Σ σ >=2S.
By above structure, such as first the 1st fluid flows in the distributing pipe 61 as cylindrical bulkhead 59 from the entrance 11 of the 1st fluid, flowing in importing road 63, and, outer distribution road 57 from from multiple dispensing orifice 65 to distributing pipe 61 is flowed out, and, the entrance 55 from this distribution road 57 by each stream, be assigned to each fluid flowing path, rise in each stream.
In the plate type heat exchanger of above-mentioned present embodiment, the pass importing road and multiple dispensing orifice is Σ σ >=2S, accordingly, promotes that liquid or gas-liquid are distributed to the equalization of each fluid flowing path significantly.That is, the wall part of the dispensing orifice of space between adjacent distributing pipe is each other divided into resistance body (opposed body), and the pressure distribution of fluid is homogenized, and, obtain rectification effect, promote that fluid distributes to each fluid flowing path equably.Thus, regardless of single-phase, gas-liquid two-phase, the heat exchange in each stream can both be carried out equably.Especially when gas-liquid two-phase, in distributing pipe, the 1st fluid forms annular flow, or is divided by above-mentioned wall part and easily form homogeneous flow, thus the equalization that can realize gas-liquid is distributed.
Here, the impartial distributivity obtained in the plate type heat exchanger of present embodiment is described.Fig. 8 is the line chart of the relation represented between Σ σ/S and apportionment ratio D.The transverse axis of Fig. 8 represents Σ σ/S, and the longitudinal axis represents apportionment ratio D.Apportionment ratio D is calculated by following formula (1).
[formula 1]
Here, G represents the full flow relevant to the fluid of object, and Gi represents the flow in each stream of this fluid, and n represents the stream number from distributing road branch, and i represents from distributing the stream of road branch from upstream towards which individual numeral in downstream.And Yi=(Gi/G) × 100, that is, Yi represents the apportionment ratio of each flow relative to the full flow of this fluid.M represents the Target Assignment rate becoming decile and join, m=(1/G) × (G/n) × 100.
As can be seen from Figure 8, no matter the flow of fluid is any one of high flow capacity, middle flow and low discharge, and when Σ σ/S is more than 2, the change of the apportionment ratio D of the known change relative to Σ σ/S is stably suppressed low.That is, in the scope that Σ σ/S is less than 2, relative to the change of Σ σ/S, apportionment ratio D significantly changes with curve, and on the other hand, when Σ σ/S is more than 2, apportionment ratio D is suppressed to smooth change relative to Σ σ/S.In addition, from the viewpoint of the difference of flow, known especially in the flowing of low discharge, in the scope that Σ σ/S is less than 2, significantly worsen.In addition, from the viewpoint manufactured, preferred allocation rate D is little as far as possible.It can thus be appreciated that, by making Σ σ/S be more than 2, widely in mode, especially, even if in the flowing of low discharge, also fluid can be assigned to multiple stream equably at the flow of fluid.In addition, in the enforcement of reality, Σ σ/S is the scope of 2 ~ 3 degree.
In addition, when becoming Σ σ >=L/d ' × π (d/2) ^2, the effect of the above-mentioned next door part for the formation of homogeneous flow can not be obtained, therefore the equalization distribution of gas-liquid becomes difficulty, and adjacent dispensing orifice may be communicated with, the difficulty of processing improves, thus processing charges increase.In the present embodiment, by adopting L/d ' × π (d/2) ^2 > Σ σ, the problems referred to above can be suppressed.
In addition, in the present embodiment, as described above more than 60% in multiple dispensing orifice is formed facing downward.About the advantage of described mode, as shown in Figure 9.Fig. 9 and Fig. 8 is same, relevant to the relation between Σ σ/S and apportionment ratio D, and, be represent the line chart towards produced difference by dispensing orifice.From the result of Fig. 9, no matter the flow of fluid is any one of high flow capacity, middle flow and low discharge, dispensing orifice mode down (shown in dotted line), compared with the dispensing orifice mode (as shown by the solid line) that to be more than 60% be not down, apportionment ratio improves further.Especially, the mode that flow is lower, the degree of improvement of apportionment ratio is larger.This is because, the liquid that what density was large be easily trapped in imports the downside on road flows out successively from the inflow entrance side of the length direction of distributing pipe, thus the liquid measure that can reduce in the flowing of the inboard of the length direction of distributing pipe, easily liquid measure is remained in distributing pipe, the homogenising of the pressure distribution of length direction can be realized, accordingly, promote that gas-liquid is distributed to the equalization of each stream.Especially, inferior in the situation of low discharge, situation that flow velocity is low, under the state that can not maintain annular flow, dispensing orifice down time, steam flows out from the downside of liquid holdup, and thus, drawn by this steam, liquid also flows out, gas-liquid mixed and flowing out in heterogeneity.In addition, even if when single-phase flow, the Temperature Distribution of the length direction produced because of bias current is homogenising by the homogenising of pressure distribution, can realize impartial distribution.
In addition, in the present embodiment, the diameter d of multiple dispensing orifice ' be configured to 40 ~ 100% of the orientation size h of fluid flowing path respectively.Thereby, it is possible to realize distributing to the equalization of each stream, and tool has the following advantages, and because the resistance of dispensing orifice is little, so when flow reduces, also can keep impartial and distribute.
Above, plate type heat exchanger according to the present embodiment, widely in mode, can both be assigned to multiple stream by fluid at the flow of fluid equably.In addition, the refrigerating circulatory device that this plate type heat exchanger uses as the evaporimeter in kind of refrigeration cycle and condenser can also be implemented, thereby, it is possible to obtain the high refrigerating circulatory device of the excellent reliability of heat exchange performance by the present invention.
Above, specifically illustrate content of the present invention with reference to preferred embodiment, but based on basic technological thought of the present invention and enlightenment, as those skilled in the art, adopt various alter mode to be apparent.
The invention is not restricted to situation about implementing as plate type heat exchanger, the heat exchanger on the distribution road that the fluid flowing path that can be widely applicable for the heat exchange with multiple arrangement is communicated with their entrance, such as, can also implement as flat tube heat exchanger.
The explanation of Reference numeral
1 plate type heat exchanger, heat transfer plate on front side of in the of 7, heat transfer plate on rear side of in the of 9,51 stream forming portions, 53 distribute road forming portion, 55 entrances, and 57 distribute road, 59 cylindrical bulkhead, 61 distributing pipes, and 63 import road, 65 dispensing orifices.
Claims (4)
1. a heat exchanger, is characterized in that, has stream forming portion, distributes road forming portion and cylindrical bulkhead,
Described stream forming portion has the fluid flowing path of multiple arrangement;
The distribution road that the respective entrance that described distribution road forming portion has described multiple fluid flowing path is communicated with;
Described cylindrical bulkhead is arranged in the forming portion of described distribution road, and described distribution road is positioned at outside the periphery of described cylindrical bulkhead, and marks off importing road in the inner side of described cylindrical bulkhead,
Described cylindrical bulkhead has the multiple dispensing orifices being communicated with described importing road and described distribution road respectively,
The flow path cross sectional area on described importing road is being set to S, the flow diameter on described importing road is set to d, the summation of the area σ of described multiple dispensing orifice is set to Σ σ, the spread length of described multiple dispensing orifice is set to L, when the diameter of described dispensing orifice is set to d ', meet
L/d’×π(d/2)＾2＞Σσ≥2S。
2. heat exchanger as claimed in claim 1, is characterized in that, the diameter d of described multiple dispensing orifice ' be respectively 40 ~ 100% of the orientation size h of described fluid flowing path.
3. heat exchanger as claimed in claim 1 or 2, it is characterized in that, described stream forming portion is stacked multiple by being formed with the concavo-convex heat transfer plate of multiple row, and described in every a pair, between heat transfer plate, be alternately formed with the 1st stream and the 2nd stream, heat exchange is carried out between the 1st fluid circulated in multiple described 1st stream and the 2nd fluid circulated in multiple described 2nd stream
Described multiple fluid flowing path is described multiple 1st stream.
4. a refrigerating circulatory device, is characterized in that, has carried the heat exchanger according to any one of claims 1 to 3.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2012/065505 WO2013190617A1 (en) | 2012-06-18 | 2012-06-18 | Heat exchanger |
| JPPCT/JP2012/065505 | 2012-06-18 | ||
| PCT/JP2013/066215 WO2013191056A1 (en) | 2012-06-18 | 2013-06-12 | Heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104380027A true CN104380027A (en) | 2015-02-25 |
Family
ID=49768248
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380032095.9A Pending CN104380027A (en) | 2012-06-18 | 2013-06-12 | Heat exchanger |
| CN201320347144.5U Expired - Lifetime CN203479101U (en) | 2012-06-18 | 2013-06-18 | Heat exchanger and refrigeration circulating device carrying same |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320347144.5U Expired - Lifetime CN203479101U (en) | 2012-06-18 | 2013-06-18 | Heat exchanger and refrigeration circulating device carrying same |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20150168081A1 (en) |
| EP (1) | EP2878911B1 (en) |
| JP (1) | JPWO2013191056A1 (en) |
| CN (2) | CN104380027A (en) |
| WO (2) | WO2013190617A1 (en) |
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| EP2977704B1 (en) * | 2013-03-22 | 2020-06-17 | Mitsubishi Electric Corporation | Plate-type heat exchanger and refrigeration cycle device with same |
| DE102015010289A1 (en) * | 2015-08-08 | 2017-02-09 | Modine Manufacturing Company | Plate heat exchanger |
| US9909822B2 (en) * | 2016-02-08 | 2018-03-06 | Hamilton Sundstrand Corporation | Channel guide distributor |
| CN108759299A (en) * | 2018-06-08 | 2018-11-06 | 常熟国和新材料有限公司 | A kind of resin aqueous emulsion cooling device |
| DE102018129988A1 (en) * | 2018-07-09 | 2020-01-09 | Hanon Systems | Compact heat exchanger unit and air conditioning module, especially for electric vehicles |
| JP1653095S (en) * | 2018-11-26 | 2020-02-17 | ||
| WO2020110685A1 (en) * | 2018-11-26 | 2020-06-04 | 三菱電機株式会社 | Plate-type heat exchanger and heat-pump-type hot-water supply system |
| JP1653096S (en) * | 2018-11-26 | 2020-02-17 | ||
| JP1653094S (en) * | 2018-11-26 | 2020-02-17 | ||
| WO2020246412A1 (en) * | 2019-06-05 | 2020-12-10 | 株式会社日阪製作所 | Plate heat exchanger and distributor for plate heat exchanger |
| JP7093800B2 (en) | 2020-02-10 | 2022-06-30 | ダイキン工業株式会社 | Heat exchanger and heat pump system with it |
| WO2023175926A1 (en) * | 2022-03-18 | 2023-09-21 | 三菱電機株式会社 | Outdoor machine for air conditioning device and air conditioning device |
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- 2013-06-12 JP JP2014521373A patent/JPWO2013191056A1/en active Pending
- 2013-06-12 CN CN201380032095.9A patent/CN104380027A/en active Pending
- 2013-06-12 WO PCT/JP2013/066215 patent/WO2013191056A1/en active Application Filing
- 2013-06-12 US US14/404,152 patent/US20150168081A1/en not_active Abandoned
- 2013-06-18 CN CN201320347144.5U patent/CN203479101U/en not_active Expired - Lifetime
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2878911A4 (en) | 2016-06-01 |
| US20150168081A1 (en) | 2015-06-18 |
| WO2013190617A1 (en) | 2013-12-27 |
| CN203479101U (en) | 2014-03-12 |
| WO2013191056A1 (en) | 2013-12-27 |
| EP2878911B1 (en) | 2019-08-28 |
| JPWO2013191056A1 (en) | 2016-05-26 |
| EP2878911A1 (en) | 2015-06-03 |
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