CN203785330U - Plate heat exchanger and refrigeration circulation device with plate heat exchanger - Google Patents
Plate heat exchanger and refrigeration circulation device with plate heat exchanger Download PDFInfo
- Publication number
- CN203785330U CN203785330U CN201420068680.6U CN201420068680U CN203785330U CN 203785330 U CN203785330 U CN 203785330U CN 201420068680 U CN201420068680 U CN 201420068680U CN 203785330 U CN203785330 U CN 203785330U
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- stream
- cowling panel
- fluid
- via hole
- heat exchanger
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- 238000005057 refrigeration Methods 0.000 title abstract description 3
- 239000012530 fluid Substances 0.000 claims abstract description 81
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 59
- 238000005476 soldering Methods 0.000 claims description 8
- 230000033228 biological regulation Effects 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 abstract 1
- 238000010586 diagram Methods 0.000 description 27
- 230000000694 effects Effects 0.000 description 13
- 239000003507 refrigerant Substances 0.000 description 7
- 230000009467 reduction Effects 0.000 description 6
- 230000003321 amplification Effects 0.000 description 4
- 238000003199 nucleic acid amplification method Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
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- 238000009826 distribution Methods 0.000 description 2
- 238000007710 freezing Methods 0.000 description 2
- 230000008014 freezing Effects 0.000 description 2
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- 239000004215 Carbon black (E152) Substances 0.000 description 1
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- 230000003467 diminishing effect Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 229930195733 hydrocarbon Natural products 0.000 description 1
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- 238000000034 method Methods 0.000 description 1
- 238000009928 pasteurization Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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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
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
- F25B39/022—Evaporators with plate-like or laminated elements
-
- 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
-
- 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
-
- 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
- F28F3/06—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being attachable to the element
-
- 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
-
- 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
- F28F9/0278—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 stacked distribution plates or perforated plates arranged over end plates
-
- 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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/043—Condensers made by assembling plate-like or laminated elements
-
- 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
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
Abstract
The utility model provides a plate heat exchanger and a refrigeration circulation device with the plate heat exchanger. The plate heat exchanger is characterized in that first flow paths and second flow paths are alternately formed between a plurality of heat transfer plates arranged at specified intervals, inner fins are arranged in the first flow paths and the second flow paths, the heat transfer plates respectively comprise upstream side path holes and downstream side path holes, the upstream side path holes become inlets for first fluid to flow into the first flow paths or inlets for second fluid to flow into the second flow paths, the downstream path holes become outlets for the first fluid to flow from the first flow paths or outlets for the second fluid to flow from the second flow paths, rectifying plates used for separating each flow path into the upstream side path hole sides and inner fin sides are respectively arranged in the first flow paths and the second flow paths, in addition, the rectifying plates are brazed onto the heat transfer plates and are provided with a plurality of opening parts becoming the flow paths of the first fluid or the second fluid, and the opening area of the opening parts is regulated so that the flow path resistance generated by the rectifying plates at one side, with a short-distance from the upstream side path holes, in the rectifying plates is smaller than the flow path resistance generated by the rectifying plates at the long-distance side.
Description
Technical field
The utility model relates to plate type heat exchanger and has the refrigerating circulatory device of this plate type heat exchanger.Background technology
In the past, proposed a kind of plate type heat exchanger of cascade type, multiple heat transfer plates are stacked across inner fin, in the each stream being formed between heat transfer plate and heat transfer plate, alternately make different fluids flow, carry out heat exchange (for example,, with reference to patent documentation 1～3) by heat transfer plate.
This plate type heat exchanger has the via hole of the entrance that becomes fluid, and the fluid flowing into from via hole is by inner fin, but in inner fin from via hole away from the flow velocity of a side slack-off, the flow velocity that approaches a side of via hole accelerates.Thus, in stream, velocity flow profile easily occurs, the delay portion that slow-footed region becomes fluid, can not bring into play function as heat-transfer area, and in addition, mobile bias current increases the pressure loss.Therefore,, in patent documentation 1～3, there is the velocity flow profile of making and become uniform rectification part.
[prior art document]
[patent documentation]
[patent documentation 1] Japanese clear 59-229193 communique (the 6th page, Fig. 4)
[patent documentation 2] Japanese clear 63-140295 communique (the 6th page, Fig. 1)
[patent documentation 3] TOHKEMY 2001-41676 communique (the 2nd page, the 3rd page, Fig. 8～10)
The rectification part of above-mentioned patent documentation 1,2 all intricately combines multiple plate-shaped members and forms, and has the problem difficult, cost is high of making.
The rectification part of patent documentation 3 is to cut a plate-shaped member to be shaped, or bending process plate-shaped member and forming repeatedly, seeks the further simplification of structure.
Utility model content
The utility model is made in view of this, its objective is and provides and can make uniformly plate type heat exchanger and have the refrigerating circulatory device of this plate type heat exchanger cheaply of velocity flow profile by simple structure.
The content of first aspect of the present utility model is a kind of plate type heat exchanger, between the spaced multiple heat transfer plates with regulation, alternately form the first stream and the second stream, in described the first stream and described the second stream, inner fin is set respectively, it is characterized in that, described multiple heat transfer plates have respectively: the upstream side via hole of body to the entrance of described the first stream or second fluid to the entrance of described the second stream gains the first rank, with become the downstream via hole of described first fluid from the outlet of described the first stream or described second fluid from the outlet of described the second stream, described in each, in the first stream and described the second stream, configure the cowling panel that each stream is separated into described upstream side via hole side and described inner fin side, and by soldering on described heat transfer plate, described cowling panel has the multiple peristomes that become the stream of described first fluid or described second fluid, and adjust the aperture area of described multiple peristomes, so that compared with a side of the near distance of described upstream side via hole, the flow path resistance being produced by described cowling panel of a side far away diminishes.
Second aspect of the present utility model is the plate type heat exchanger on the basis of first aspect, compares with a side of the near distance of described cowling panel and described upstream side via hole, and the interval between described cowling panel and the described inner fin of a side far away is short.
The third aspect of the present utility model is the plate type heat exchanger on the basis of first aspect or second aspect, compare with a side of the near distance of described multiple peristomes and described upstream side via hole, the aperture area the earth of described multiple peristomes of a side far away forms.
Fourth aspect of the present utility model is the plate type heat exchanger on the basis of first aspect or second aspect, described multiple peristome is configured to identical size, configuration number in the described cowling panel of described multiple peristomes, in described cowling panel, compare with a side of the near distance of described cowling panel and described upstream side via hole, the configuration number of a side far away is many.
The 5th aspect of the present utility model is the plate type heat exchanger on the basis of first aspect or second aspect, and described inner fin is biasing fin.
The 6th aspect of the present utility model is the plate type heat exchanger on the basis of first aspect or second aspect, between described downstream via hole and described inner fin, also has the cowling panel identical with described cowling panel.
The 7th aspect of the present utility model is the plate type heat exchanger on the basis of first aspect or second aspect, the identical and different cowling panel of total aperture area of the shape also between described downstream via hole and described inner fin with described cowling panel and described multiple peristomes.
Eight aspect of the present utility model is the plate type heat exchanger on the basis aspect the 7th, with in two described cowling panels that possessed pass through described cowling panel time total open area ratio of the low described cowling panel of fluid density described in the large mode of total aperture area of the high described cowling panel of fluid density, be formed with described multiple peristomes separately of two described cowling panels.
The 9th aspect of the present utility model is the plate type heat exchanger on the basis of first aspect, described cowling panel also has from described cowling panel and the two ends orthogonal direction of decoupled direction along a pair of shank mutually extending concurrently with the orthogonal direction of described cowling panel, and described a pair of shank becomes the composition surface with described heat transfer plate.
The content of the tenth aspect of the present utility model is a kind of plate type heat exchanger, between stacked multiple heat transfer plates, alternately form the first stream and the second stream, in described the first stream and described the second stream, inner fin is set respectively, it is characterized in that, described in each, multiple heat transfer plates have: the upstream side via hole of body to the entrance of described the first stream or second fluid to the entrance of described the second stream gains the first rank, with become the downstream via hole of described first fluid from the outlet of described the first stream or described second fluid from the outlet of described the second stream, described in each, in the first stream and described the second stream, configure the cowling panel that each stream is separated into described upstream side via hole side and described inner fin side, and by this cowling panel soldering on described heat transfer plate, described cowling panel has the peristome extending along the decoupled direction of described cowling panel, described peristome is adjusted aperture area, so that compared with a side of the near distance of described upstream side via hole, the flow path resistance being produced by described cowling panel of a side far away diminishes.
The content of the tenth one side of the present utility model is a kind of plate type heat exchanger, between stacked multiple heat transfer plates, alternately form the first stream and the second stream, in described the first stream and described the second stream, inner fin is set respectively, it is characterized in that, described multiple heat transfer plates have respectively: the upstream side via hole of body to the entrance of described the first stream or second fluid to the entrance of described the second stream gains the first rank; With become the downstream via hole of described first fluid from the outlet of described the first stream or described second fluid from the outlet of described the second stream, described in each, in the first stream and described the second stream, configure the cowling panel that each stream is separated into described upstream side via hole side and described inner fin side, and by this cowling panel soldering on described heat transfer plate, described cowling panel, in described cowling panel, compared with a side of the near distance of described upstream side via hole, the height lowland of the described cowling panel of a side far away forms.
The content of the 12 aspect of the present utility model is a kind of refrigerating circulatory device, it is characterized in that, has the plate type heat exchanger described in first aspect or second aspect.
Plate type heat exchanger of the present utility model is by the configuration of cowling panel, can obtain making velocity flow profile plate type heat exchanger cheaply uniformly simply to construct.
Brief description of the drawings
Fig. 1 is the figure that represents the general inner fin plate-type heat exchanger in embodiment of the present utility model.
Fig. 2 is the figure of an example of the inner fin 2 of presentation graphs 1.
Fig. 3 is the key position amplification stereogram of Fig. 1.
Fig. 4 is the key diagram of the cowling panel 30 of Fig. 3, is the front view of cowling panel 30.
Fig. 5 is the key diagram of the cowling panel 30 of Fig. 3, is the cutaway view along the A-A line of Fig. 4.
Fig. 6 is the key diagram of the cowling panel 30 of Fig. 3, is the side view of cowling panel 30.
Fig. 7 is the key diagram of the modified example 1 of the cowling panel 30 of Fig. 1, is the front view of cowling panel 30.
Fig. 8 is the key diagram of the modified example 1 of the cowling panel 30 of Fig. 1, is the cutaway view along the A-A line of Fig. 7.
Fig. 9 is the key diagram of the modified example 1 of the cowling panel 30 of Fig. 1, is the side view of cowling panel 30.
Figure 10 is the key diagram of the modified example 2 of the cowling panel 30 of Fig. 1, is the front view of cowling panel 30.
Figure 11 is the key diagram of the modified example 2 of the cowling panel 30 of Fig. 1, is the cutaway view along the A-A line of Figure 10.
Figure 12 is the key diagram of the modified example 2 of the cowling panel 30 of Fig. 1, is the side view of cowling panel 30.
Figure 13 is the key diagram of the modified example 3 of the cowling panel 30 of Fig. 1, is the front view of cowling panel 30.
Figure 14 is the key diagram of the modified example 3 of the cowling panel 30 of Fig. 1, is the cutaway view along the A-A line of Figure 13.
Figure 15 is the key diagram of the modified example 3 of the cowling panel 30 of Fig. 1, is the side view of cowling panel 30.
Figure 16 is the key diagram of the modified example 4 of the cowling panel 30 of Fig. 1, is the front view of cowling panel 30.
Figure 17 is the key diagram of the modified example 4 of the cowling panel 30 of Fig. 1, is the top view of cowling panel 30.
Figure 18 is the key diagram of the modified example 4 of the cowling panel 30 of Fig. 1, is the side view of cowling panel 30.
Figure 19 is the key diagram of the modified example 5 of the cowling panel 30 of Fig. 1, is the front view of cowling panel 30.
Figure 20 is the key diagram of the modified example 5 of the cowling panel 30 of Fig. 1, is the cutting portion end-view along the A-A line of Figure 19.
Figure 21 is the key diagram of the modified example 5 of the cowling panel 30 of Fig. 1, is the side view of cowling panel 30.
Figure 22 is the key position amplification stereogram of the plate type heat exchanger of embodiment 2 of the present utility model.
Figure 23 is the stereogram of the plate type heat exchanger of embodiment 3 of the present utility model.
Figure 24 is the stereogram of the modified example of the plate type heat exchanger of embodiment 3 of the present utility model.
Figure 25 is the figure that represents the refrigerant loop of the refrigerating circulatory device of embodiment 4 of the present utility model.
The explanation of Reference numeral
1 heat transfer plate, 2 inner fins, 3 side plates, 4 inflow pipes, 5 effusers, 6 inflow pipes, 7 effusers, 11 first openings, 12 second openings, 13 the 3rd openings, 14 the 4th openings, 20a upstream side via hole, 20b downstream via hole, 21 closure, 30 cowling panels, 31 peristomes, 31a peristome, 31b peristome, 32 shanks, 40 refrigerating circulatory devices, 41 compressors, 42 condensers, 43 throttling arrangements, 44 evaporimeters, A the first stream, A1 region, A2 region, B the second stream, M region.
Detailed description of the invention
Embodiment 1
Fig. 1 is the figure that represents the general inner fin plate-type heat exchanger of embodiment of the present utility model.Fig. 2 is the figure of an example of the inner fin 2 of presentation graphs 1.Fig. 3 is the key position amplification stereogram of Fig. 1.In Fig. 1～Fig. 3 and accompanying drawing described later, the parts that mark same Reference numeral are identical or suitable with it parts, and this is general in the full text of description.And the form of the constitutive requirements of describing in description full text is exemplary, is not limited to these records.
Inner fin plate-type heat exchanger (being designated hereinafter simply as " sheet heat exchanger ") has multiple heat transfer plates 1 of smooth heat-transfer area.Multiple heat transfer plates 1 arrange with the interval of regulation, are alternately formed with the first stream A flowing for first fluid and the second stream B flowing for second fluid between multiple heat transfer plates 1.In Fig. 1, using the flow direction of first fluid as x, using the flow direction of second fluid as y.And, in the first stream A and the second stream B, be respectively arranged with the inner fin 2 that promotes heat transfer.In addition, be provided with the side plate 3 of performance booster action at the both ends of the stacked direction of multiple heat transfer plates 1, engaged integratedly on the whole together with multiple heat transfer plates 1 and inner fin 2.
Inner fin 2 adopts biasing fin (オ Off セ ッ ト Off ィ Application) here.Biasing fin has following structure, that is, in wave-shaped fins, each prescribed distance of the length direction of tooth paddy (mountain valley) pressing board of plate width direction respectively staggers half tooth and is formed as zigzag on plate width direction.
Multiple heat transfer plates 1 and two side plates 3 are made up of the flat board of metal essentially rectangular, and four jiaos of the side in two side plates 3 are provided with the inflow pipe 4 of first fluid, effuser 5, the inflow pipe 6 of second fluid and the effuser 7 of second fluid of first fluid.
In addition, on heat transfer plate 1, in the position corresponding with the effuser 7 of the inflow pipe 6 of the effuser 5 of the inflow pipe 4 of first fluid, first fluid, second fluid, second fluid, be formed with respectively the first opening 11, the second opening 12, the 3rd opening 13 and the 4th opening 14.These first openings 11, the second opening 12, the 3rd opening 13, the 4th opening 14 are formed with respectively the inflow entrance of the first stream A, the flow export of the first stream A, the inflow entrance of the second stream B, the flow export of the second stream B.
In heat transfer plate 1, around the first opening 11 and the second opening 12 or the 3rd opening 13 and the 4th opening 14, be provided with closure 21(with reference to Fig. 3).This closure 21 is to seal the 3rd opening 13 and the 4th opening 14 in the first stream A flowing for first fluid, in the second stream B flowing for second fluid, seals the first opening 11 and the second opening 12.Like this, second fluid is prevented to the inflow of the first stream A, and first fluid is prevented to the inflow of the second stream B.
Below, the opening being communicated with inner fin 2 being formed in 4 openings of heat transfer plate 1 is called to via hole.Therefore, in the first stream A, the first opening 11 and the second opening 12 become via hole, and in the second stream B, the 3rd opening 13 and the 4th opening 14 become via hole.In addition, below, the via hole that becomes fluid intake in two via holes that are arranged on a heat transfer plate 1 is called to upstream side via hole 20a, the via hole that becomes fluid issuing is called to downstream via hole 20b.In addition, below, in the situation that not distinguishing the first stream A and the second stream B, referred to as stream.Similarly, in the situation that not distinguishing first fluid and second fluid, referred to as fluid.
Flow into from upstream side via hole 20a stream fluid flow velocity in general, accelerate near of upstream side via hole 20a, slack-off at a distance.Thus, in the region M of the distance apart from upstream side via hole 20a, fluid is difficult to flow, fluid retention.Therefore, from region M downstream the flow of the fluid of side flow tail off, thereby effectively heat transfer area diminishes.
For improve with the width (the X-Y direction of Fig. 3) of such heat transfer plate 1 on the assignment of traffic followed of the biasing of velocity flow profile inhomogeneous, adopt following structure., in the first stream A and the second stream B, between upstream side via hole 20a and inner fin 2, be configured for and make flow velocity tabular cowling panel 30 uniformly respectively.Cowling panel 30 is configured on heat transfer plate 1 in the mode of separating between upstream side via hole 20a and inner fin 2.
Fig. 4, Fig. 5, Fig. 6 are the key diagrams of the cowling panel 30 of Fig. 3, and Fig. 4 is front view, and Fig. 5 is that Fig. 6 is side view along the cutaway view of the A-A line of Fig. 4.In addition, Fig. 4 is the key diagram for the feature of the cowling panel 30 of key diagram 3, and quantity, the engineer's scale etc. of peristome 31 is not corresponding with Fig. 3 closely.This is also same in the key diagram of cowling panel 30 described later.
On cowling panel 30, the decoupled direction (length direction of cowling panel 30) of cowling panel 30 spaced apart be formed with multiple peristomes 31.Cowling panel 30 adjust multiple peristomes 31 aperture area in case in cowling panel 30 along with diminishing from the flow path resistance that tends to a side fairing 30 far away with a side of the near distance of upstream side via hole 20a.Specifically, in cowling panel 30, be positioned at from the order of the position of a side direction of the near distance of a upstream side via hole 20a side far away, the aperture area of multiple peristomes 31 becomes the earth and forms.
In Fig. 4, multiple peristome 31(31a, 31b) be configured to circle here, form greatlyr than the diameter of the peristome 31b apart from the near region A2 side of upstream side via hole 20a apart from the diameter of the peristome 31a of upstream side via hole 20a region A1 side far away.In addition, here, with two stages adjustment aperture areas, but be not limited to two stages, also can adopt the more multistage.
By this structure, it is larger than the aperture area of each peristome 31b that is positioned at the region A2 side near apart from upstream side via hole 20a that the aperture area that is positioned at each peristome 31a of the region A1 side far away apart from upstream side via hole 20a becomes.Therefore, in cowling panel 30, to become the region A2 side faster than flow velocity little for the flow path resistance of the slow region A1 side of flow velocity, and in the M of region, fluid easily flows.Thus, can make the flow velocity of X-Y direction even, can improve the delay of the fluid in the M of region.Its result can be brought into play function as heat-transfer area using the downstream part of region M, thereby can expand effective heat transfer area in heat transfer plate 1.
Here, the length L 1 of the X-Y direction of the region A1 of the earth formation peristome 31 is shorter than the equidirectional length L 2 of closure 21.The stream being formed by closure 21 and cowling panel 30 is narrower than the stream between upstream side via hole 20a and cowling panel 30, is difficult to flow to region M.Thus, the region of the L1 that resistance is little is set on cowling panel 30, but L1 is when larger than L2, before fluid inflow region M, the peristome 31 in the L1 of side nearby flows out, and it is difficult that the homogenising of speed becomes.Make L1 less than L2, compared with the situation of L1 > L2, can realize the further homogenising of speed thus.
Closure 21 becomes the resistance of the fluid mobile to region M, but the utility model is by carrying out the adjustment of the aperture area on cowling panel 30, can adjust to the direction that the recruitment of the pressure loss being produced by this resistance is eliminated.Thus, be effective for the improvement of the biasing of velocity flow profile.In addition, the shape of each peristome 31 is not limited to circle, also can adopt square, rectangle etc.In addition, in Fig. 4, the diameter of each peristome 31a of region A1 is all identical, in the A2 of region, also makes the diameter of each peristome 31b identical, but also can be along with leaving from upstream side via hole 20a, and it is large that diameter becomes gradually.
Here, suppose in the situation that there is no cowling panel 30, the flow velocity being produced by bias current rises becomes the increase essential factor of the pressure loss.But by configuration cowling panel 30, the flow velocity that can suppress to be produced by bias current rises, thereby can realize the reduction of the pressure loss.
As mentioned above, in present embodiment 1, between the upstream side via hole 20a and inner fin 2 that are arranged at heat transfer plate 1, separate the tabular cowling panel 30 of both ground configurations.And, on cowling panel 30, decoupled direction spaced apart multiple peristomes 31 are set.And, adjust the aperture area of multiple peristomes 31, so that the flow path resistance of fluid during by cowling panel 30, little with a side far away compared with the near side of upstream side via hole 20a.Thus, can make velocity flow profile even, can improve the biasing of the flow of the entrance side of inner fin 2, can realize the expansion of effective heat transfer area and the reduction of the pressure loss.
In addition, because cowling panel 30 is simple structures of perforate only on plate-shaped member, so make simply, can realize the expansion of effective heat transfer area and the reduction effect of the pressure loss with low cost, in addition, can realize lightweight.
In addition, because cowling panel 30 is simple structures of perforate only on plate-shaped member, also become easy for the big or small adjustment that makes velocity flow profile become uniform each peristome 31.In addition, although even make cowling panel 30 by single part, be also at a low price, while shaping integratedly with inner fin 2, part number reduces, thereby becomes more at a low price.In addition, cowling panel 30 can engage with heat transfer plate 1 by soldering, and can manufacture sheet heat exchanger by one soldering qurer.
In addition, in cowling panel 30, peristome 31 part is each other the effect that next door has the fluid mixing that has made to pass through peristome 31, has good effect for the homogenising of flow velocity.
In addition, because cowling panel 30 erects and configures in the mode between separation upstream side via hole 20a and inner fin 2, so in the time carrying out improving the arranging of cowling panel 30 of mechanism's performance function as distribution, do not need wide space, can arrange with few space.
In addition, in the situation that cowling panel 30 is not set, easily producing the region M being detained is the slow part of flow velocity of fluid.Thus, fluid is water, and in situation about using plate type heat exchanger as evaporimeter, temperature reduces partly, becomes the starting point of freezing.But, in present embodiment 1, because the flow velocity that can make the fluid in the M of region rises, so can suppress to freeze, can realize quality and improve.
Like this, because the sheet heat exchanger of present embodiment 1 has high heat transfer, low pressure loss, the such effect of high reliability, so also can use the CO that evaporability is little
2cold-producing medium, the combustible refrigerant such as hydrocarbon, low GWP cold-producing medium that the pressure loss is large.
In addition, because inner fin 2 has used biasing fin, so can obtain following effect.Biasing fin is that the heat transfer of low pressure loss promotes body, because resistance is little, so fluid is easily with streamlined flow.Thus, in hypothesis cowling panel 30 is not set, fluid is not in the situation of inflow region M, and in the region of swim more on the lower than region M, fluid is mobile hardly.In this case, effectively heat transfer area diminishes as described above.But, by the biasing fin of low pressure loss is used as heat-transfer area, and then combine with cowling panel 30, can realize thus the reduction of the pressure loss and the effectively expansion of heat transfer area.
In addition, by the leading edge effect of biasing fin, can, in improving heat transfer, suppress the rising of the pressure loss.In addition, leading edge effect refers to utilizes the character that heet transfer rate is good in dull and stereotyped leading edge portion, the effect that can realize dull and stereotyped exterior region as hot transfer part use energetically.That is to say, when flat board is placed in flow region, in dull and stereotyped leading edge, the thin thickness of interlayer, the thickening along with trend downstream.Thus, the thin thickness of interlayer, in dull and stereotyped leading edge portion, heat transmission becomes good.
In addition, the heat transfer plate 1 of cowling panel 30, biasing fin, smooth heat-transfer area can be made by punching press respectively, can manufacture low pressure loss and the high plate type heat exchanger of heat transfer property by qurer.When plate type heat exchanger is low pressure loss, the required power of the action of fluid diminishes.Thus, can reduce to become the pump of power source and the capacity of compressor that make fluid flow into plate type heat exchanger.
In addition,, although in the situation that inner fin 2 has used biasing fin, can obtain above-mentioned effect, inner fin of the present utility model is not limited to the fin of setovering.In addition, inner fin 2 of the present utility model not only comprise with heat transfer plate 1 split the fin that forms, also comprise and make the surface of heat transfer plate 1 become the fin that the ground such as such as waveform form.
In addition, the entrance side that the equalization of flow is distributed in stream is essential, and does not need at outlet side.Therefore, do not arrange at entrance side and outlet side both sides, only at entrance side, cowling panel 30 is set, can become thus low cost.
In addition, number, shape, the configuration of the peristome 31 of cowling panel 30 are not limited to the structure shown in Fig. 1, and for example following modified example 1～4 can be implemented various shifting grounds in this wise.Modified example all has following structure arbitrarily,, forms multiple or 1 peristome 31 that is, so that the flow path resistance when the cowling panel 30, compared with approaching a side of upstream side via hole 20a, a side far away diminishes.In modified example arbitrarily, all there is the effect of the homogenising of flow velocity.
(modified example 1)
Fig. 7, Fig. 8, Fig. 9 are the key diagrams of the modified example 1 of the cowling panel 30 of Fig. 3, and Fig. 7 is front view, and Fig. 8 is that Fig. 9 is side view along the cutaway view of the A-A line of Fig. 7.
In Fig. 5, although respectively in region A1 and region A2, be provided with multiple peristomes 31, peristome 31(31a, a 31b also can be set in region A1 and region A2 respectively).And in Fig. 5, the shape that shows peristome 31 adopts rectangular example.And, in this structure, also with Fig. 4～Fig. 6 similarly, compared with peristome 31b apart from the near region A2 side of upstream side via hole 20a, can make the aperture area of the peristome 31a of the region A1 side far away apart from upstream side via hole 20a increase.
(modified example 2)
Figure 10, Figure 11, Figure 12 are the key diagrams of the modified example 2 of the cowling panel 30 of Fig. 3, and Figure 10 is front view, and Figure 11 is that Figure 12 is side view along the cutaway view of the A-A line of Figure 10.
In Fig. 4～Fig. 6, although respectively in region A1 and region A2, make the diameter difference of peristome 31, in Figure 10～Figure 12, adopt all identical diameters, along with from upstream side via hole 20a away from, the configuration number of peristome 31 is increased.In addition, in the above description, from this side direction of the near distance of upstream side via hole 20a away from a side, the aperture area of peristome 31 becomes large with two stages, but stage quantity is not limited to two stages, and the example in 3 stages has been shown in Figure 10～Figure 12.
(modified example 3)
Figure 13, Figure 14, Figure 15 are the key diagrams of the modified example 3 of the cowling panel 30 of Fig. 3, and Figure 13 is front view, and Figure 14 is that Figure 15 is side view along the cutaway view of the A-A line of Figure 13.
In Figure 13～Figure 15, peristome 31 arranges 1, and in cowling panel 30, along with from tending to a side far away with a side of the near distance of upstream side via hole 20a, it is large that aperture area becomes.
(modified example 4)
Modified example 4 is the external form shapes according to cowling panel 30, the flow path resistance during by cowling panel 30 part, and with compared with the near side of upstream side via hole 20a, a side far away is little.
Figure 16, Figure 17, Figure 18 are the key diagrams of the modified example 4 of the cowling panel 30 of Fig. 3, and Figure 16 is front view, and Figure 17 is top view, and Figure 18 is side view.
The cowling panel 30 of Figure 16～Figure 18 is in cowling panel 30, and along with from tending to a side far away with a side of the near distance of upstream side via hole 20a, the height step-down ground of the cowling panel 30 of stacked direction (left and right directions of Fig. 1) forms.
Cowling panel 30 shown in Fig. 3～Figure 18 also can adopt simply tabular, but forms also can the modified example 5 shown in following Figure 19.
(modified example 5)
Figure 19, Figure 20, Figure 21 are the key diagrams of the modified example 5 of the cowling panel 30 of Fig. 3, and Figure 19 is front view, and Figure 20 is that Figure 21 is side view along the cutting portion end-view of the A-A line of Figure 19.
This cowling panel 30 has following structure, that is, the two ends that are provided with width from cowling panel 30 (with the orthogonal direction of decoupled direction) are along a pair of shank 32 mutually extending concurrently with the orthogonal direction of cowling panel 30.
By respectively using this pair of shank 32 as with the composition surface of heat transfer plate 1, thus, cowling panel 30 becomes pillar.And, by adjusting the length of a pair of shank 32, can adjust according to necessary intensity the area on the composition surface of a pair of shank 32 and heat transfer plate 1.Thus, correspondingly adjust the length of a pair of shank 32 with the desired intensity of via hole periphery a little less than peel strength, and a pair of shank 32 of having adjusted is used as composition surface, thus, the intensity of upstream side via hole 20a periphery can be brought up to necessary intensity.
In addition, when cowling panel 30 is configured as to the shape of Figure 19～Figure 21, while making by punching press, owing to making by a punching press, thus can be with low cost fabrication.
Embodiment 2
Embodiment 2 is about the configuration of cowling panel 30, different from embodiment 1.About point in addition, identical with embodiment 1.In addition, about the applicable modified example of the component part identical with embodiment 1, be suitable for similarly for present embodiment 2.
Figure 22 is the key position amplification stereogram of the plate type heat exchanger of embodiment 2 of the present utility model.
In embodiment 2, along with tend to the mode that a side far away shortens from the near side of upstream side via hole 20a, cowling panel 30 is arranged on obliquely heat transfer plate 1 with the interval of cowling panel 30 and inner fin 2.
By forming like this, can obtain the effect same with embodiment 1, and the fluid that flows into stream from upstream side via hole 20a can be guided to region M.Thus, as Embodiment 1, than configuring orthogonally cowling panel 30 with flow direction, fluid becomes easily and flows to region M.Thus, the adjustment of the aperture area of the peristome 31 in embodiment 1, the angle adjustment of the inclination of the cowling panel 30 by embodiment 2, can also more carefully carry out the adjustment of velocity flow profile.
Embodiment 3
In above-mentioned embodiment 1,2, in the first stream A and the second stream B, between upstream side via hole 20a and inner fin 2, configure cowling panel 30 respectively.In embodiment 3, between downstream via hole 20b and inner fin 2, also configure cowling panel 30.About point in addition, identical with embodiment 1,2.In addition, about the applicable modified example of the component part identical with embodiment 1, present embodiment 2 is suitable for similarly.
Figure 23 is the stereogram of the plate type heat exchanger of embodiment 3 of the present utility model.
As shown in figure 23, between downstream via hole 20b and inner fin 2, also dispose cowling panel 30.
According to embodiment 3, can obtain the effect same with embodiment 1,2, and dispose cowling panel 30 at upstream side and downstream both sides, thus, and the not only entrance side of fluid, the distribution of outlet side is also enhanced.Thus, with only compared with the situation of the entrance configuration cowling panel 30 of fluid, about the expansion of effective heat transfer area, the reduction of the pressure loss, the inhibition of freezing, can obtain higher effect.
And, due to the gateway of cowling panel 30 in stream, so will be applicable to this plate type heat exchanger maybe can carry out aircondition that changes in temperature turn round etc. while like that the flow direction of the heat exchanger of fluid being switched to rightabout device if carry out the aircondition of changes in temperature switching simultaneously, be effective.
In addition, in plate type heat exchanger, undergoing phase transition of fluid, at entrance side and outlet side, in the situation that the density of fluid changes, also can with this variable density matchingly, at the cowling panel 30 of entrance side and the cowling panel 30 of outlet side, make total aperture area (summation of the aperture area of standard-sized sheet oral area 31) difference of peristome 31.For example, become liquid at entrance side, outlet side becomes steam and (that is to say, density ratio liquid is low, it is large that the pressure loss during by peristome 31 easily becomes) situation under, as shown in figure 24, also can make total aperture area of cowling panel 30 of total open area ratio entrance side (right side of Figure 24) of the cowling panel 30 of outlet side (left side of Figure 24) large.Thus, can realize the reduction of the pressure loss.
Embodiment 4
Embodiment 4 relates to the refrigerating circulatory device of the plate type heat exchanger arbitrarily that has adopted embodiment 1～embodiment 3.
Figure 25 is the figure that represents the refrigerant loop of the refrigerating circulatory device 40 of embodiment 4 of the present utility model.
Refrigerating circulatory device 40 is the general refrigerating circulatory devices with compressor 41, condenser (air inclusion cooler) 42, throttling arrangement 43 and evaporimeter 44.And, as the condenser 42 of refrigerating circulatory device 40 and a side of evaporimeter 44 or two sides, adopt the plate type heat exchanger arbitrarily of embodiment 1～embodiment 3.
According to present embodiment 4, by the plate type heat exchanger of embodiment 1～embodiment 3 is set, can obtain the high and refrigerating circulatory device 40 cheaply of energy saving and reliability.In addition, the refrigerant loop shown in Figure 25 is an example, adopts the refrigerant loop of plate type heat exchanger of the present utility model to be not limited to the structure of Figure 25.For example, can be also cross valve to be set and can to switch refrigeration or the refrigerant loop that heats, can be also to carry out refrigerant loop that changes in temperature turn round simultaneously etc.
Industrial applicibility
As the example of applying flexibly of the present utility model, pasteurization treatment facility that can be used in air-conditioning, generating, food etc. has carried a large amount of industry of plate type heat exchanger, home-use equipment.
Claims (12)
1. a plate type heat exchanger alternately forms the first stream and the second stream between the spaced multiple heat transfer plates with regulation, in described the first stream and described the second stream, inner fin is set respectively, it is characterized in that,
Described multiple heat transfer plate has respectively: the upstream side via hole of body to the entrance of described the first stream or second fluid to the entrance of described the second stream gains the first rank; With become the downstream via hole of described first fluid from the outlet of described the first stream or described second fluid from the outlet of described the second stream,
Described in each, in the first stream and described the second stream, each stream is separated into the cowling panel of described upstream side via hole side and described inner fin side by configuration, and by this cowling panel soldering on described heat transfer plate,
Described cowling panel has the multiple peristomes that become the stream of described first fluid or described second fluid, and adjust the aperture area of described multiple peristomes, so that compared with a side of the near distance of described upstream side via hole, the flow path resistance being produced by described cowling panel of a side far away diminishes.
2. plate type heat exchanger as claimed in claim 1, is characterized in that, compares with a side of the near distance of described cowling panel and described upstream side via hole, and the interval between described cowling panel and the described inner fin of a side far away is short.
3. plate type heat exchanger as claimed in claim 1 or 2, is characterized in that, compares with a side of the near distance of described multiple peristomes and described upstream side via hole, and the aperture area the earth of described multiple peristomes of a side far away forms.
4. plate type heat exchanger as claimed in claim 1 or 2, is characterized in that,
Described multiple peristome is configured to identical size,
Configuration number in the described cowling panel of described multiple peristomes is compared with a side of the near distance of described cowling panel and described upstream side via hole in described cowling panel, and the configuration number of a side far away is many.
5. plate type heat exchanger as claimed in claim 1 or 2, is characterized in that, described inner fin is biasing fin.
6. plate type heat exchanger as claimed in claim 1 or 2, is characterized in that, between described downstream via hole and described inner fin, also has the cowling panel identical with described cowling panel.
7. plate type heat exchanger as claimed in claim 1 or 2, is characterized in that, the identical and different cowling panel of total aperture area of the shape also between described downstream via hole and described inner fin with described cowling panel and described multiple peristomes.
8. plate type heat exchanger as claimed in claim 7, it is characterized in that, with in two described cowling panels that possessed pass through described cowling panel time total open area ratio of the low described cowling panel of fluid density described in the large mode of total aperture area of the high described cowling panel of fluid density, be formed with described multiple peristomes separately of two described cowling panels.
9. plate type heat exchanger as claimed in claim 1 or 2, it is characterized in that, described cowling panel also has from described cowling panel and the two ends orthogonal direction of decoupled direction along a pair of shank mutually extending concurrently with the orthogonal direction of described cowling panel, and described a pair of shank becomes the composition surface with described heat transfer plate.
10. a plate type heat exchanger alternately forms the first stream and the second stream between stacked multiple heat transfer plates, in described the first stream and described the second stream, inner fin is set respectively, it is characterized in that,
Described in each, multiple heat transfer plates have: the upstream side via hole of body to the entrance of described the first stream or second fluid to the entrance of described the second stream gains the first rank; With become the downstream via hole of described first fluid from the outlet of described the first stream or described second fluid from the outlet of described the second stream,
Described in each, in the first stream and described the second stream, each stream is separated into the cowling panel of described upstream side via hole side and described inner fin side by configuration, and by this cowling panel soldering on described heat transfer plate,
Described cowling panel has the peristome extending along the decoupled direction of described cowling panel,
Described peristome is adjusted aperture area, so that compared with a side of the near distance of described upstream side via hole, the flow path resistance being produced by described cowling panel of a side far away diminishes.
11. 1 kinds of plate type heat exchangers alternately form the first stream and the second stream between stacked multiple heat transfer plates, in described the first stream and described the second stream, inner fin are set respectively, it is characterized in that,
Described multiple heat transfer plate has respectively: the upstream side via hole of body to the entrance of described the first stream or second fluid to the entrance of described the second stream gains the first rank; With become the downstream via hole of described first fluid from the outlet of described the first stream or described second fluid from the outlet of described the second stream,
Described in each, in the first stream and described the second stream, each stream is separated into the cowling panel of described upstream side via hole side and described inner fin side by configuration, and by this cowling panel soldering on described heat transfer plate,
Described cowling panel, in described cowling panel, compared with a side of the near distance of described upstream side via hole, the height lowland of the described cowling panel of a side far away forms.
12. 1 kinds of refrigerating circulatory devices, is characterized in that, have the plate type heat exchanger described in claim 1 or 2.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2013/058210 WO2014147804A1 (en) | 2013-03-22 | 2013-03-22 | Plate-type heat exchanger and refrigeration cycle device with same |
| JPPCT/JP2013/058210 | 2013-03-22 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203785330U true CN203785330U (en) | 2014-08-20 |
Family
ID=51321508
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420068680.6U Expired - Lifetime CN203785330U (en) | 2013-03-22 | 2014-02-18 | Plate heat exchanger and refrigeration circulation device with plate heat exchanger |
Country Status (5)
| Country | Link |
|---|---|
| EP (1) | EP2977704B1 (en) |
| JP (1) | JP6091601B2 (en) |
| CN (1) | CN203785330U (en) |
| HK (1) | HK1216114A1 (en) |
| WO (1) | WO2014147804A1 (en) |
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| CN110651164A (en) * | 2017-05-23 | 2020-01-03 | 三菱电机株式会社 | Plate heat exchanger and heat pump type hot water supply system |
| CN110651164B (en) * | 2017-05-23 | 2021-04-20 | 三菱电机株式会社 | Plate heat exchanger and heat pump type hot water supply system |
| CN109149325A (en) * | 2018-09-21 | 2019-01-04 | 清华大学 | A kind of mixed structure micro-channel heat sink |
| CN109149325B (en) * | 2018-09-21 | 2019-11-22 | 清华大学 | A kind of mixed structure micro-channel heat sink |
| CN112997045A (en) * | 2018-11-16 | 2021-06-18 | 三菱电机株式会社 | Plate heat exchanger, heat pump device, and heat pump type cooling/heating hot water supply system |
| WO2021177668A1 (en) * | 2020-03-05 | 2021-09-10 | 한온시스템 주식회사 | Plate-type heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| HK1216114A1 (en) | 2016-10-14 |
| EP2977704A1 (en) | 2016-01-27 |
| WO2014147804A1 (en) | 2014-09-25 |
| EP2977704A4 (en) | 2017-02-01 |
| EP2977704B1 (en) | 2020-06-17 |
| JPWO2014147804A1 (en) | 2017-02-16 |
| JP6091601B2 (en) | 2017-03-08 |
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