CN1101418A - Plate heat exchanger for fluids of different flow - Google Patents
Plate heat exchanger for fluids of different flow Download PDFInfo
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- CN1101418A CN1101418A CN 93118905 CN93118905A CN1101418A CN 1101418 A CN1101418 A CN 1101418A CN 93118905 CN93118905 CN 93118905 CN 93118905 A CN93118905 A CN 93118905A CN 1101418 A CN1101418 A CN 1101418A
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- heat transfer
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Abstract
The plate-type heat exchanger for two kinds of fluid in different flows comprises several almost square heat-transfer plates with inlet and outlet through corners and each heat-transfer plate has one central heat-transfer portion and two distribution portions between heat-transfer portion and inlet-outlet. The sizes of inlet and outlet are different for different fluids, and so does the flowing resistances.
Description
The present invention relates to be used for the heat-exchangers of the plate type that conducts heat between the fluid of two kinds of different flows, this heat exchanger is made of the heat transfer plate that several piece is substantially rectangle, each piece heat transfer plate all has and passes the import and export that its bight is used for various fluids, one in central authorities the heat transfer part between import and export separately, with two dispenser, these two dispenser and are used for the distribution of these two kinds of fluids when heat transfer part flows from its import at these fluids between heat transfer part and import and export separately.
Traditional shaping heat-exchangers of the plate type generally has one group of identical heat transfer plate, and these heat transfer plates have identical import and export for two kinds of fluids.A kind of like this heat exchanger with identical import and export preferably only is used for two kinds of fluids of same traffic.If wherein a kind of fluid passes through the flow of heat exchanger less than one other fluid, then the pressure drop of fluid will be different, and its reason is square pro rata variation of pressure drop with the volume flow.In other words, if the flow difference of fluid, then the effect of the heat transfer between fluid and the heat transfer plate on the two sides of every heat transfer plate can not be best.
For asymmetric the flowing between the so-called heat-exchange fluid, in order to increase heat transfer, the someone advised reducing the volume of flow-catheter on heat transfer plate one side in the past, in being disclosed in European patent EP 470073, being advised, perhaps the combination of the different ripple structions by heat transfer plate influences the flow resistance of flow-catheter, as being disclosed on European patent EP 88316 or the EP204880.Usually the structure of these previous suggestions is only allowed little asymmetric flowing between two kinds of fluids, and for two kinds of fluids, the heat transmission on the heat transfer plate is not sufficiently effective.
The objective of the invention is in the heat-exchangers of the plate type of mentioned kind, between the fluid of two kinds of different flows, to obtain a kind of improved heat-transfer effect.Another object of the present invention is to propose a kind of heat-exchangers of the plate type that is used for the fluid of different flow, compares with previously known board-like heat exchange, and this heat exchanger can be allowed big asymmetric flowing between two kinds of fluids of different flow.
The object of the present invention is achieved like this, the size of import and export opening of heat transfer plate of first kind of fluid that is used in described two kinds of fluids is less than the import and export opening size that is used for one other fluid, and heat transfer plate is being processed on its dispenser in the flow resistance of the first fluid that flows between the import and export of first kind of fluid and the heat transfer part flow resistance greater than the one other fluid that flows between the import and export of second fluid and heat transfer part.
Although the flow of two kinds of heat-exchange fluids is different, the objective of the invention is to make on the both sides of heat transfer plate have same big pressure drop.Therefore, for instance, the heat transfer flow condition of first kind of fluid (fluid that promptly has minimum discharge) is optimized, and the flox condition of one other fluid (fluid that promptly has maximum stream flow) is simplified simultaneously.
Preferably do the flow channel on each dispenser of first kind of fluid longer, make the flow resistance of the flow resistance of first kind of fluid greater than one other fluid than the flow channel on each dispenser of one other fluid.
And can make the flow resistance of the flow resistance of first kind of fluid with the runner overall width of dispenser that is used for first kind of fluid less than the overall width of one other fluid greater than one other fluid.
Also can be by on the dispenser of heat transfer plate, designing punching structure, make press depth on the side of each heat transfer plate less than the press depth on another side, so that two kinds of fluids have different flow resistances.In other words, the height of distribution portion can change, and promptly heat transfer plate is more shallow than the flow channel of the bigger flow side of flow channel of low discharge side.In this way, heat transfer plate has increased having the possibility that big two kinds of asymmetric mobile fluids provide available heat to transmit.
By making heat transfer plate be provided with the import and export of different size to the different fluid part, and the part is provided with a kind of punching structure on dispenser, make flow obtain wide relatively inlet end and outlet end by big aperture, and obtain narrower inlet end and outlet end by flow than microstome, the flow that flows through big aperture can increase, and the flow that flows through microstome then reduces.Therefore, heat transfer plate admits of a kind of strong asymmetry between two kinds of different flows, provides the flox condition that helps conducting heat between the fluid for two kinds of fluids simultaneously.
Details are as follows to the present invention below with reference to accompanying drawings, among the figure:
Fig. 1 schematically shows heat-exchangers of the plate type of the present invention;
Fig. 2 shows first kind of heat transfer plate of the heat-exchangers of the plate type that is used for Fig. 1;
Fig. 3 shows second kind of heat transfer plate of the heat-exchangers of the plate type that is used for Fig. 1;
Fig. 4 shows the another kind of heat transfer plate that is used for heat-exchangers of the plate type of the present invention.
Heat-exchangers of the plate type 1 shown in Fig. 1 comprises one group of thin 2, front end-plates 3 of heat transfer plate and end plate 4.Be useful on than an import 5 and an outlet 6 of first kind of fluid of low discharge on the front end-plate 3 and be used for an import 7 and an outlet 8 of second kind of fluid of big flow.
The first heat transfer plate 2a shown in Fig. 2 is elongated and roughly becomes rectangle, has import 5a, 7a and outlet 6a and 8a on it respectively.Import and outlet all are positioned at bight 9a, 10a, 11a and the 12a of heat transfer plate.The import of first kind of fluid and outlet 5a and 6a are positioned at long limit 13a one side of heat transfer plate, another long limit 14a one side that the import and export 7a of one other fluid and 8a are positioned at heat transfer plate.Heat transfer plate 2a is designed to PARALLEL FLOW, and promptly the main flow direction of fluid on each side of heat transfer plate is parallel.
According to the present invention, the import and export 5a and the 6a of first kind of fluid are identical, but are generally less than the import and export 7a and the 8a of one other fluid.Equally, importing and exporting 7a also is identical with 8a.
In addition, heat transfer plate 2a has one and goes up dispenser 15a, a following dispenser 16a and be arranged in heat transfer part 17a between them.
Have punching structure on last dispenser 15a and the following dispenser 16a, these structures roughly are to form according to the content among the BP No.1357282.Therefore, they have mutually near the lug boss 18a that stretches out, these lug bosses are that the punching press that makes progress from a plane that is parallel to heat transfer plate 2a forms, and stretch out groove 19a near what the downward punching press from above-mentioned plane formed mutually with lug boss 18a is angled.Because groove 19a is formed with lug boss on the another side of heat transfer plate 2a, so, lug boss is all arranged on the two sides of heat transfer plate, these lug bosses are formed for the passage of heat transfer fluid with middle board in each side of dispenser 15a and 16a.The passage that is formed on like this on heat transfer plate one side becomes skewed with the passage that forms in the same manner on the opposite side of heat transfer plate.
From Fig. 2, can see significantly, protruding 18a shown in each dispenser 15a and the 16a on the side is basically extending towards the direction of heat transfer part 17a from big opening 7a and 8a, and groove 19a is basically to extend towards the direction of heat transfer part 17a from smaller opening 5a and 6a.
The punching structure that heat transfer part 17a shows is the so-called projection of routine and the herringbone pattern of groove.
Shown the second heat transfer plate 2b in Fig. 3, in heat-exchangers of the plate type of the present invention, this heat transfer plate cooperates with heat transfer plate 2a shown in Figure 2.Some of heat transfer plate 2b in detail part (in heat transfer plate 2a, also can find) use with Fig. 2 in same numeral represent that but the back is with " b " replacement " a ".
In heat transfer plate 2b, the 18a of respective protrusions portion among the heat transfer plate 2a among the lug boss 18b on each dispenser 15b and the 16b and groove 19b and Fig. 2 compares in another way with groove 19a and forms.Therefore, lug boss 18b extends with the direction from relatively little opening 5b and 6b towards heat transfer part 17b basically, and groove 19b is basically to extend towards the direction of heat transfer part 17b from bigger opening 7b and 8b.
And aspect the direction of the projection of herringbone pattern punching press and groove, the heat transfer part 17b of heat transfer plate 2b is different from the heat transfer part 17a of heat transfer plate 2a correspondence.
When two heat transfer plate 2a and 2b in heat-exchangers of the plate type mutually altogether the time, on each dispenser 15a, the 16a of heat transfer plate and 15b, 16b zone, wherein the lug boss on heat transfer plate will extend in parallel on the lug boss that leans against on another piece heat transfer plate.On heat transfer part 17a and 17b zone, the herringbone lug boss of heat transfer plate will be close mutually across, form a so-called corrugated-crossed structure.
Heat transfer part cooperates the two heat transfer plates flow direction that a kind of fluid flows between heat transfer plate that produces corrugated-crossed structure to observe, and is formed with many pure angles between cross one another lug boss, therefore provides very large flow resistance to this kind fluid.In this case, because this geometry of heat transfer plate, although the flowing velocity on the dispenser zone is about the twice of the flowing velocity on the main heat transfer part zone, the general precentagewise of the dispenser of heat transfer plate is resolutely little to the influence of the flow resistance in the middle of the heat transfer plate.
Heat transfer part with herringbone pattern forms corresponding acute angle between cross one another lug boss, provide a little flow resistance on the contrary with above-mentioned situation, and dispenser the influence to flow resistance can the proportional increase of precentagewise between plate.
According to the present invention, the flow resistance by making big flow is less than the flow resistance than low discharge, illustrated the asymmetry between two kinds of heat-exchange fluid flows.This is to make the import and export that are used for big flow on the heat transfer plate greater than the import and export that are used for low discharge, and it is wideer shorter to be used in the dispenser of big flow, but prolongs and reduced the width of low discharge accordingly.
For example, in dispenser 15a and 16a, fluid flow by bigger import and export 7a and 8a obtains wide import and export end, and the total flow width that promptly is used for big flow on heat transfer plate one side is bigger, and is used for less than total flow width of low discharge on this side of heat transfer plate.
In addition, it is longer to compare the flow channel of the dispenser 15a that is used for low discharge and 16a with big flow.
In the punching structure of the dispenser of kind shown in Fig. 2 and Fig. 3, be used for big traffic channel (in a side of heat transfer plate) circulation area can by will the board between last stamped bumps and the following stamped recess place from the bottom of groove than doing more from the top of projection is nearer, but correspondingly reduced to be used for the circulation area of low discharge passage (at the opposite side of this heat transfer plate).
The heat transfer plate 20 that in Fig. 4, has shown another kind of design, this heat transfer plate is different from the heat transfer plate 2a shown in Fig. 2, its import 25 that is used for first kind of fluid is positioned at 21 places, a long limit of heat transfer plate, and the outlet 26 that is used for this same fluid is positioned at 22 places, the second long limit of heat transfer plate; The import 27 that is used for second kind of fluid is positioned at 21 places, a long limit of heat transfer plate, and the outlet 28 that is used for second kind of fluid is positioned at 22 places, the second long limit of heat transfer plate.This heat transfer plate 20 is designed to so-called mobile to angie type, and promptly the main flow direction of these fluids intersects mutually, and each fluid streams flows through heat transfer plate 20 diagonally.
Flow about the diagonal angle, in heat-exchangers of the plate type, require two kinds of different types of heat transfer plates (having different punching structures) that desirable cooperation is provided between the punching structure of adjacent panels.According to the present invention, on heat transfer plate, carry out the flow function of the middle heat transfer part of (Fig. 4) and dispenser of diagonal angle and all be similar to the heat transfer plate of PARALLEL FLOW (Fig. 2 and Fig. 3).
About PARALLEL FLOW, the heat-exchangers of the plate type that the present invention proposes can be only obtains by means of a kind of plate that is provided with identical punching structure on dispenser and heat transfer part, as long as another kind of plate is changeed 180 ° around an axis on this board plane with respect to other plate.But this just requires structurally to be useful on the specific condition that seals between two plates along the edge of heat transfer plate with around its import and export.
The open end that is used for big flow in the dispenser zone of heat transfer plate is wideer by 50% than the open end that is used for low discharge, the passage that is used for low discharge is longer by 50% than the passage that is used for big flow, doubles than the channel capacity that is used for low discharge when the channel capacity that the two combination can be used in big flow has identical pressure drop between two kinds of fluids are by each piece plate.
Low discharge is being adopted more shallow passage, big flow is being adopted in the combination of darker passage, the asymmetric ratio in the dispenser zone between the small-large flow is 3: 1.
When heat transfer part has the herringbone structure of band acute angle, thereby when less flow resistance was provided, the ratio that can obtain heat-exchange fluid by whole heat-exchangers of the plate type was 3: 1.
When heat transfer part has herringbone structure with pure angle, thereby when bigger flow resistance was provided, the ratio by obtainable heat-exchange fluid between the small-large flow of heat-exchangers of the plate type was 1.2-1.5: 1.
In the heat-exchangers of the plate type that the present invention proposes, can keep the pressure drop of the heat-exchange fluid that flows on the heat transfer plate both sides, irrelevant with different flows.This just might make the runner that has than the fluid of low discharge have than on heat transfer plate that corresponding runner has less circulation area in the conventional heat-exchangers of the plate type of import and export of identical size.With regard to this respect, the fluid course with big flow can be obtained than the bigger circulation area of runner corresponding in conventional heat-exchangers of the plate type.Because this point, the heat-exchangers of the plate type that the present invention proposes obtains the flow bigger than conventional heat-exchangers of the plate type in big flow side partly, obtains than having the relevant bigger heat-transfer capability of conventional heat-exchangers of the plate type of certain asymmetry with the flow of heat-exchange fluid partly.
This bigger heat-transfer capability of heat transfer plate can be used in a different manner, perhaps in some heat exchange work, the heat-exchangers of the plate type that the present invention proposes can use the heat transfer plate that lacks than conventional heat-exchangers of the plate type, perhaps makes each piece heat transfer plate do than littler with the heat transfer plate of conventional method design.In the later case, except the cost of heat transfer plate, the cost that is used for pivot frame that in groups heat transfer plate is fixed together also can reduce.For instance, at latter event, elongated heat transfer plate formed according to the present invention can be done thinlyyer than corresponding conventional heat transfer plate.And framework can be done thinlyyer thus, thereby more cheap.
One of the present invention is also advantageous in that the flow simplification effect of asymmetry of fluid can stand under the situation of ability of high fluid pressure and carry out not damaging heat transfer plate, and the thinness of keeping heat transfer plate simultaneously is constant.The strong point between the heat transfer plate can be arranged closely as conventional heat transfer plate with contact point.
Above only a kind of punching structure of the dispenser of heat transfer plate and a kind of punching structure of heat transfer part have been done introduction, but as the back appending claims limited, within the scope of the invention, some other suitable punching structure can be arranged.
Claims (6)
1, a kind of heat-exchangers of the plate type of conducting heat between the fluid of two kinds of different flows of being used for, this heat exchanger comprises that several piece is roughly the heat transfer plate (2a of rectangle, 20), every heat transfer plate all has and passes import and export (5a, 6a and 7a, the 8a that its bight is used for various fluids; 25,26 and 27,28); Heat transfer part (17a) between each is imported and exported in central authorities; And be positioned at dispenser (15a, 16a) between heat transfer part (17a) and the corresponding import and export, when these fluids by their import when heat transfer part flows, dispenser is used to distribute two kinds of corresponding fluids; It is characterized in that: import and export (5a, the 6a of heat transfer plate that is used for first kind of fluid of described two kinds of fluids; 25,26) size is than the import and export that are used for one other fluid (7a, 8a; 27,28) size is little, and on their dispenser, heat transfer plate forms at the import and export of first kind of fluid (5a, 6a; The flow resistance of the first kind of fluid that flows 25,26) and between the heat transfer part (17a) is than import and export (7a, 8a at second kind of fluid; The flow resistance of the one other fluid that flows 27,28) and between the heat transfer part (17) is big.
2, heat-exchangers of the plate type as claimed in claim 1, the runner that it is characterized in that being used on the dispenser (15a, 16a) of first kind of fluid is longer than the runner on the dispenser that is used for one other fluid (15a, 16a).
3, heat-exchangers of the plate type as claimed in claim 1 is characterized in that: the total flow width of dispenser (15a, 16a) that is used for first kind of fluid is narrower than total flow width of the dispenser that is used for one other fluid.
4, heat-exchangers of the plate type as claimed in claim 1, it is characterized in that: the punching structure of dispenser (15a, 16a) makes that the press depth on the side of heat transfer plate (2a, 20) is littler than the press depth on the opposite side, thereby makes the runner of first kind of fluid more shallow than the runner of one other fluid.
5, heat-exchangers of the plate type as claimed in claim 1, it is characterized in that: described heat transfer plate is elongated, import and export (the 5a that is used for first kind of fluid, 6a) a long limit (13a) that is positioned at each piece heat transfer plate is located, and the import and export (7a, 8a) that are used for one other fluid are positioned at the second long limit (14a) of each piece heat transfer plate and locate.
6, heat-exchangers of the plate type as claimed in claim 1 is characterized in that: the position arrangement of the import and export of heat transfer plate (25-28) intersects and diagonal angle extension on heat transfer plate two main flow directions that the fluid between the heat transfer plate flows mutually.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 93118905 CN1053040C (en) | 1993-10-06 | 1993-10-06 | Plate heat exchanger for fluids of different flow |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 93118905 CN1053040C (en) | 1993-10-06 | 1993-10-06 | Plate heat exchanger for fluids of different flow |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1101418A true CN1101418A (en) | 1995-04-12 |
| CN1053040C CN1053040C (en) | 2000-05-31 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 93118905 Expired - Fee Related CN1053040C (en) | 1993-10-06 | 1993-10-06 | Plate heat exchanger for fluids of different flow |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1053040C (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102356295A (en) * | 2009-03-18 | 2012-02-15 | 三菱电机株式会社 | Plate-type heat exchanger and refrigerating air-conditioning device |
| CN102958723A (en) * | 2010-10-07 | 2013-03-06 | 三菱重工业株式会社 | Heat-medium heating device and vehicle air conditioning device provided with same |
| CN105806108A (en) * | 2015-01-19 | 2016-07-27 | 中央大学 | Heat exchange module |
| CN108139182A (en) * | 2015-10-02 | 2018-06-08 | 阿尔法拉瓦尔股份有限公司 | Heat transfer plate and plate heat exchanger |
| CN110553524A (en) * | 2018-05-30 | 2019-12-10 | 丹佛斯有限公司 | Plate heat exchanger for desalination system |
| CN112444149A (en) * | 2019-08-30 | 2021-03-05 | 浙江三花智能控制股份有限公司 | Plate heat exchanger |
| US11486657B2 (en) | 2018-07-17 | 2022-11-01 | Tranter, Inc. | Heat exchanger heat transfer plate |
-
1993
- 1993-10-06 CN CN 93118905 patent/CN1053040C/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102356295A (en) * | 2009-03-18 | 2012-02-15 | 三菱电机株式会社 | Plate-type heat exchanger and refrigerating air-conditioning device |
| CN102356295B (en) * | 2009-03-18 | 2015-10-14 | 三菱电机株式会社 | Heat-exchangers of the plate type and refrigerating air-conditioning |
| CN102958723A (en) * | 2010-10-07 | 2013-03-06 | 三菱重工业株式会社 | Heat-medium heating device and vehicle air conditioning device provided with same |
| CN105806108A (en) * | 2015-01-19 | 2016-07-27 | 中央大学 | Heat exchange module |
| CN105806108B (en) * | 2015-01-19 | 2018-07-13 | 中央大学 | Heat exchange module |
| CN108139182A (en) * | 2015-10-02 | 2018-06-08 | 阿尔法拉瓦尔股份有限公司 | Heat transfer plate and plate heat exchanger |
| CN108139182B (en) * | 2015-10-02 | 2019-07-12 | 阿尔法拉瓦尔股份有限公司 | Heat transfer plate and plate heat exchanger |
| US10724802B2 (en) | 2015-10-02 | 2020-07-28 | Alfa Laval Corporate Ab | Heat transfer plate and plate heat exchanger |
| CN110553524A (en) * | 2018-05-30 | 2019-12-10 | 丹佛斯有限公司 | Plate heat exchanger for desalination system |
| US11486657B2 (en) | 2018-07-17 | 2022-11-01 | Tranter, Inc. | Heat exchanger heat transfer plate |
| CN112444149A (en) * | 2019-08-30 | 2021-03-05 | 浙江三花智能控制股份有限公司 | Plate heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1053040C (en) | 2000-05-31 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20000531 Termination date: 20091106 |