CN2097998U - Unequal-sectional plate type heat exchanger - Google Patents
Unequal-sectional plate type heat exchanger Download PDFInfo
- Publication number
- CN2097998U CN2097998U CN 91210893 CN91210893U CN2097998U CN 2097998 U CN2097998 U CN 2097998U CN 91210893 CN91210893 CN 91210893 CN 91210893 U CN91210893 U CN 91210893U CN 2097998 U CN2097998 U CN 2097998U
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- China
- Prior art keywords
- heat exchanger
- plate
- cold
- plate type
- type heat
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Abstract
The utility model discloses a plate type heat exchanger. Cold and heat medium passage areas which are formed by two adjacent heat exchange plate sheets of the plate type heat exchanger are in a certain proportion. Thus, under the condition that the proportion of the flow quantities of the cold and heat mediums is 2: 1 or other ratios, the flow velocities of the cold and heat mediums can be equal when the flow velocities all reach to maximum allowable velocities, and pipe lines are all installed on one side. The shapes of the corrugated edges of the plate sheets can be trapezoids, circle arcs, triangles, triangles with pleats, etc. The plate type heat exchanger has the advantages of high efficiency, convenient installation, convenient disassembly, convenient cleaning, convenient maintenance, and low cost.
Description
The utility model relates to a kind of improvement of plate type heat exchanger.
Plate type heat exchanger is to be the high-performance heat exchanger of heat-transfer area with the corrugated plating.At present, the plate type heat exchanger of each manufacturer production of home and abroad, although plurality of specifications and form are arranged, all ripple rib of plate is all by same size and shape-designing manufacturing.As Beijing China heating exchange device factory all, what 1989 the 3rd interim " application problem of plate type heat exchanger in central heating system " literary compositions of " district heating " that the product of productions such as heating exchange device factory, Tianjin and Chinese urban heating association publish were introduced all is so, and the hot and cold medium channel area that promptly produced plate is formed equates.
As everyone knows, improve the coefficient of heat transfer of heat exchanger, must make these two kinds of flow rate of fluid of hot and cold medium maintain an equal level as far as possible, equate.Adopt the present heat exchanger that waits aisle spare, if when medium is a water-water, have only when hot water or cold water's flow-rate ratio is 1:1, the flow velocity of cold water is just equal with the flow velocity of hot water.In the present domestic central heating system, hot water or cold water's flow-rate ratio all requires to be 2:1-2.5:1.Therefore, in order to improve the heat exchange efficiency of heat exchanger, make cold, the flow velocity of hot water maintains an equal level as far as possible, equate, foreign data proposes to adopt following two kinds of designs, first kind is cold medium single process, thermal medium double fluid journey form, its advantage is only a heat exchanger to be set, make cold, the way that the flow process number of hot water becomes 1:2 solves, its shortcoming is cold, thermal medium flow wherein that some is the following current heat transfer, the temperature difference and heat transfer coefficient between the heat exchanging fluid have been reduced, thereby partly offset and improved the desired benefit of flow velocity, its disadvantage also is also to connect on the removable cover and has gone up pipeline, and this brings very big inconvenience for heat exchanger disassembly, cleaning and daily maintenance.Another kind of scheme is for forming the form of cold medium parallel connection, thermal medium series connection with two heat exchangers, though it has overcome the shortcoming of first kind of scheme, but an equipment changes two into, this has not only increased floor space, also cover stands that increased, this Outer Tube connect comparatively more, and complexity also is a big shortcoming of this scheme.
The general form that adopts single process in the present domestic central heating system.Like this, hot water or cold water's flow velocity just can not equate that naturally the flow velocity of hot water approximately is 0.5 times of cold water flow velocity, and like this, obviously heat exchanger is in the lower state of the coefficient of heat transfer.
The purpose of this utility model just provides a kind of hot and cold rate-of flow than for 2:1 or other ratios, the new-type plate type heat exchanger that single process and hot and cold velocity of medium equate.
Principle of the present utility model is such: the ripple rib on the heat transferring plate of heat exchanger such as is made at the pitch of waves, but adjacent two ripple ribs cun is proportional plate to the greatest extent.During assembling, adjacent plate except Rotate 180 °, the upset of still needing, the sectional area of formed like this adjacency channel also is proportional, promptly is not prismatic.As being water-water when hot and cold medium, and hot water or cold water's flow is when being 2:1, and the plate of design makes the sectional area ratio of the adjacent formed hot and cold passage of plate become 2:1.When hot water or cold water's flow ratio expanded other ratios to, the plate of design made the formed hot and cold channel cross-sectional area of adjacent plate than arriving 3:1 for 1.5:1.When using such heat exchanger, hot water or cold water's flow velocity maintains an equal level, and can both reach the maximum of permission, makes heat exchanger running status the best.At this moment adopt equipment of form of single process to get final product.Its hot water or cold water's import and export pipeline is installed in clamping plate one side.
Further specify below in conjunction with embodiment
The long-pending heat exchanger channel sectional view of formed unequal section when Fig. 1 is trapezoidal for plate ripple rib, (1) is the heat exchanger plate; (2) be cold medium channel; (3) be hot media channel.
The long-pending heat exchanger channel sectional view of formed unequal section when Fig. 2 is circular arc for plate ripple rib.(4) be the heat exchanger plate; (5) be cold medium channel; (6) be hot media channel.
Fig. 3 connects form for the plate type heat exchanger pipeline.(7) be cold media outlet, (8) are the thermal medium import; (9) be the thermal medium outlet; (10) be cold medium import; (11) be clamping plate; (12) be fishbolt.
In central heating system, hot water or cold water's out temperature is at present domestic to reach unanimity substantially:
Hot water: import: 110-130 ℃; Outlet: 60-70 ℃;
Cold water: outlet: 80-90 ℃; Import: 55-60 ℃.
In heat exchanger, (△ th)/(△ tc)=(mc)/(mh), △ t in the formula
c, △ t
hBe respectively the import and export temperature difference of hot and cold water; m
c, m
hBe respectively hot water or cold water's flow.At this moment, can calculate hot and cold rate-of flow than (mc)/(mh)=2:1.When therefore we designed plate, adjacent channel cross-sectional area was than being 2:1.That the ripple prismatic shape of plate can be selected is trapezoidal, the triangle of circular arc type, triangle, band pleat etc., explanation respectively below.
When 1, the ripple rib is trapezoidal:
As shown in Figure 1, plate (1) is all made same size, specification, is that cold medium channel (2) and hot media channel (3) are designed to unequal section, wherein b
1Can be at b
1Select b between the=2-3.5mm
2Can be at b
2Select between=the 6-8.5mm, pitch of waves t is chosen for t=12-16mm; Wave height H is chosen for H=3.5-4.5mm.As select H=3.8mm, b
1=2.5mm, b
2=7mm, then pitch of waves t
1=13mm, the ratio of the area of formed cold medium channel of the plate of making (1) (2) and hot media channel (3) is 2:1.Satisfied the flow-rate ratio of above-mentioned requirements, when flow-rate ratio changes, can adopt sectional area ratio to equal flow-rate ratio, determine wave height H after, calculate b by the trapezoidal area formula
1And b
2Ratio, then from above-mentioned b
1And b
2Get b in the span
1And b
2Value.
When 2, the ripple rib is circular arc,
As shown in Figure 2, when design plate (4), after wave height H determines, adjust R
1And R
2Ratio, the area that makes cold medium channel (5) and hot media channel (6) is than equating with flow-rate ratio.R
1And R
2Span be respectively R
1=5-12mm, R
2=2-7mm.
In when assembling, adjacent plate (1) or plate (4) be plane Rotate 180 ° at first, and then overturns 180 °, is fixed together at last, and a slice a slice is formed the heat exchanger that whole unequal section amasss like this.
Heat exchanger of the present utility model, its pipeline connect all the side at heat exchanger, as scheming shown in (3), on clamping plate (11), have four passwaies, promptly cold media outlet (7), thermal medium import (8), thermal medium outlet (9), cold medium import (10).
Plate type heat exchanger of the present utility model, guaranteeing that hot and cold rate-of flow is under the situation of 2:1 or other ratios, the flow velocity of hot and cold medium all obtains to equate reaching under the maximum permission speed, and pipeline is all installed in a side, like this, the efficient of plate type heat exchanger improves greatly, and pipeline is installed very easy, be convenient to heat exchanger disassembly, cleaning and daily maintenance, and greatly reduce the cost of heat exchanger.
Claims (3)
1, the plate type heat exchanger of being made up of heat transferring plate, sealing strip, clamping plate is characterized in that: the ratio of the area of two adjacent plates (1) or the cold medium channel of (4) formed hexagon (2) or the cold medium channel of garden arc (5) and hexagon hot media channel (3) or garden arc hot media channel (6) is 1.5: 1 to 3: 1.
2, plate type heat exchanger according to claim 1 is characterized in that: the ripple prismatic of plate (1) is trapezoidal, wherein adjacent two trapezoidal end b
1And b
2Span is b
1=2-3.5mm, b
2=6-8.5mm.
3, plate type heat exchanger according to claim 1 is characterized in that: the ripple prismatic of plate (4) is the garden arc, wherein adjacent two garden arc R
1And R
2Span be R
1=5-12mm, R
2=2-7mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 91210893 CN2097998U (en) | 1991-07-15 | 1991-07-15 | Unequal-sectional plate type heat exchanger |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 91210893 CN2097998U (en) | 1991-07-15 | 1991-07-15 | Unequal-sectional plate type heat exchanger |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN2097998U true CN2097998U (en) | 1992-03-04 |
Family
ID=4919647
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 91210893 Withdrawn CN2097998U (en) | 1991-07-15 | 1991-07-15 | Unequal-sectional plate type heat exchanger |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN2097998U (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101932897B (en) * | 2007-12-21 | 2013-01-30 | 阿尔法拉瓦尔股份有限公司 | Heat exchanger |
| CN105333757A (en) * | 2015-12-15 | 2016-02-17 | 浙江鸿远制冷设备有限公司 | Heat exchanger of variable-volume channel structure |
| CN105371684A (en) * | 2015-12-15 | 2016-03-02 | 浙江鸿远制冷设备有限公司 | Sheet space structure for heat exchanger |
| CN105659047A (en) * | 2013-09-17 | 2016-06-08 | 莱维尔控股公司 | Heat exchanger with improved configuration |
| CN108020106A (en) * | 2016-10-31 | 2018-05-11 | 丹佛斯微通道换热器（嘉兴）有限公司 | Plate heat exchanger as economizer |
| CN108885074A (en) * | 2016-03-30 | 2018-11-23 | 阿法拉伐股份有限公司 | Heat transfer plate and plate heat exchanger including multiple this heat transfer plates |
| CN109416223A (en) * | 2016-04-18 | 2019-03-01 | Qcip控股有限公司 | With the micro-channel evaporator for reducing pressure drop |
| CN109441640A (en) * | 2018-12-25 | 2019-03-08 | 中国船舶重工集团公司第七0三研究所 | A kind of plate-fin recuperator shell for helium turbine |
-
1991
- 1991-07-15 CN CN 91210893 patent/CN2097998U/en not_active Withdrawn
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101932897B (en) * | 2007-12-21 | 2013-01-30 | 阿尔法拉瓦尔股份有限公司 | Heat exchanger |
| CN105659047A (en) * | 2013-09-17 | 2016-06-08 | 莱维尔控股公司 | Heat exchanger with improved configuration |
| CN105333757A (en) * | 2015-12-15 | 2016-02-17 | 浙江鸿远制冷设备有限公司 | Heat exchanger of variable-volume channel structure |
| CN105371684A (en) * | 2015-12-15 | 2016-03-02 | 浙江鸿远制冷设备有限公司 | Sheet space structure for heat exchanger |
| CN105371684B (en) * | 2015-12-15 | 2017-10-13 | 浙江鸿远制冷设备有限公司 | A kind of heat exchanger plate chip architecture |
| CN108885074A (en) * | 2016-03-30 | 2018-11-23 | 阿法拉伐股份有限公司 | Heat transfer plate and plate heat exchanger including multiple this heat transfer plates |
| US10989486B2 (en) | 2016-03-30 | 2021-04-27 | Alfa Laval Corporate Ab | Heat transfer plate and plate heat exchanger comprising a plurality of such heat transfer plates |
| CN109416223A (en) * | 2016-04-18 | 2019-03-01 | Qcip控股有限公司 | With the micro-channel evaporator for reducing pressure drop |
| CN108020106A (en) * | 2016-10-31 | 2018-05-11 | 丹佛斯微通道换热器（嘉兴）有限公司 | Plate heat exchanger as economizer |
| CN109441640A (en) * | 2018-12-25 | 2019-03-08 | 中国船舶重工集团公司第七0三研究所 | A kind of plate-fin recuperator shell for helium turbine |
| CN109441640B (en) * | 2018-12-25 | 2020-11-06 | 中国船舶重工集团公司第七0三研究所 | Plate-fin regenerator shell for helium turbine |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C15 | Extension of patent right duration from 15 to 20 years for appl. with date before 31.12.1992 and still valid on 11.12.2001 (patent law change 1993) | ||
| RN01 | Renewal of patent term | ||
| C19 | Lapse of patent right due to non-payment of the annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |