CN104180693A - Novel total-reverse-flow rotary non-mixing heat exchanger - Google Patents
Novel total-reverse-flow rotary non-mixing heat exchanger Download PDFInfo
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- CN104180693A CN104180693A CN201410406850.1A CN201410406850A CN104180693A CN 104180693 A CN104180693 A CN 104180693A CN 201410406850 A CN201410406850 A CN 201410406850A CN 104180693 A CN104180693 A CN 104180693A
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- heat exchanger
- runner
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Abstract
The invention discloses a novel total-reverse-flow rotary non-mixing heat exchanger. The novel total-reverse-flow rotary non-mixing heat exchanger is characterized in that portions, except for a heat exchanger base, of the heat exchanger can rotate in service procedures, and the heat exchanger comprises a heat exchanger barrel, flow channel converters, inner seal heads of the heat exchanger, outer seal heads of the heat exchanger and the heat exchanger base; total-reverse-flow non-mixing rotary heat exchange effects can be realized for two channels of fluids, and the purpose of improving the heat exchange effects can be achieved. The heat exchanger barrel is a cylindrical barrel with two or an even number of internal barriers, the even number is larger than 2, the barrel is uniformly divided into an even number of equal portions by the barriers, a fan-shaped flow channel is formed by each left barrier, the corresponding right barrier and a cylindrical barrel portion sandwiched by the left barrier and the right barrier, and the flow channel converters are used as flow channel conversion devices. The novel total-reverse-flow rotary non-mixing heat exchanger has the advantages that the heat exchanger is used in fluid heat exchange places and is high in heat exchange efficiency, average heat exchange temperature difference and outlet temperature uniformity and free of mixing among the heat exchange fluids; the novel total-reverse-flow rotary non-mixing heat exchanger is wide in application and can be applied to heat transfer enhancement or temperature homogenization among different fluids in industrial application, and the like.
Description
Technical field
The present invention relates to a kind of novel full adverse current and rotate without direct contact heat exchanger, belong to fluid heat transfer equipment and technology category.
Background technology
Heat transfer process is very general in industrial process and daily life, is one of basic physical process of occurring in nature.It is extensively seen in as departments such as power, chemical industry, metallurgy, space flight, air-conditioning, refrigeration, machinery, light textile, buildings.Be greatly the Turbo-generator Set of 1,300,000 kilowatts to single-machine capacity, little cooling all closely related with diabatic process to microelectronic component.Heat exchanger is a kind of common apparatus of extensive use in diabatic process, and in oil refining enterprise, the equipment investment of heat exchanger accounts for 25% of gross investment, and the weight of heat exchanger accounts for 20% of gross weight of equipment amount.Taking power plant as example, the investment of the heat transmission equipments such as various boilers, condenser heater accounts for 70% of whole power plant investment.In refrigeration plant, the weight of evaporimeter, condenser also will account for the more than 30% of whole unit weight.
Due to the importance of heat exchanger in actual application, from energy-conservation angle, in order further to reduce the volume of heat exchanger, weight reduction and metal consumption, reduce the power that heat exchanger consumes, and make heat exchanger in the poor lower work of lower temperature, must strengthen the heat transfer in heat exchanger by various ways.Therefore recently for over ten years, how augmentation of heat transfer effect is the main direction in hot transfer study always.The Main Means of augmentation of heat transfer comprises following several at present: 1, increase heat exchange area, and by fin, opposite sex surface, porous mass structure, reduces the methods such as caliber and realizes; 2, increase the Average heat transfer temperature difference, realize by modes such as adverse current or cross-flow heat exchange; 3, increase overall heat-transfer coefficient, reduce heat transfer boundary layer effect, by improving gas flow rate, strengthen gas disturbance, in fluid, add solid particle, adopt the modes such as short tube heat exchanger.
The heat exchanger that heat transmission is used at present mainly contains pipe heat exchanger, plate type heat exchanger, heat-pipe heat exchanger.Heat exchanger and reinforcement technique thereof are also mainly the improvement of static structure, adopt finned tube, screwed pipe, and the technology such as pluggable unit in pipe increase heat exchange area, strengthen less turbulence, reduce heat transmission resistance.At present, also fewer for the research of dynamic heat exchanger, CN103175420A has announced a kind of core body rotary type heat exchanger, the mode that it mainly rotates by heat exchange core body, and the less turbulence of increase tubular heat exchanger shell-side fluid, reaches the object that strengthens heat transfer effect.CN202013125U has announced a kind of fluid impact rotary type heat exchanger, and its method adopting is, at the shell side of shell-and-tube heat exchanger, impeller is set, and relying on shell-side fluid to flow through vane rotary increases the disturbance of shell side, thereby reaches the object that increases heat transfer effect.The present invention has adopted fan-shaped spaced-apart flow passages design, and cold fluid and hot fluid all rotates, and for increasing the level of disruption of fluid, peels off heat transfer boundary layer, reaches the object that strengthens heat-transfer effect.
Summary of the invention
The object of the present invention is to provide a kind of novel complete mixing flow to rotate without direct contact heat exchanger, this heat exchanger, for fluid thermal exchange occasion, has heat exchange efficiency high, and heat exchange mean temperature difference is large, and the outlet temperature uniformity is high, between heat exchanging fluid without features such as mixing.
The present invention is realized by following technical proposals, a kind of novel complete mixing flow rotates without direct contact heat exchanger, it is characterized in that heat exchanger cylindrical shell 7 is that an inside has multi-piece baffle plate cylindrical tube, cylindrical shell is evenly divided into multiple even number deciles by baffle plate, and left and right sides baffle plate and middle folded cylindrical tube part thereof form a fan-shaped runner.Runner converter 5 and 6 is runner conversion equipment, structure is identical, its basic composition unit is runner converter outer baffle 6-1, runner converter Internal baffle 6-2 and runner converter dividing plate 6-3, in the left side of runner converter 6, the left side edge of outer baffle 6-1 and Internal baffle 6-2 forms a circle, circular interior is cross section E, annular section between circular outer and runner converter cylindrical shell 7 is cross section G, between the runner converter dividing plate 6-3 of Internal baffle 6-2 and its both sides and heat exchanger cylindrical shell 7, the region of composition is cross section H, the region forming between the runner converter dividing plate 6-3 of outer baffle 6-1 and both sides is cross section F.The cross section, right side of outer baffle 6-1 is a circular arc, and the right side circular arc of all outer baffles is concentric, and cross section, outer baffle 6-1 right side and heat exchanger cylindrical shell 7 coincide, and the right side edge of runner interchanger dividing plate 6-3 and heat exchanger cylindrical shell 7 baffle plate left sides coincide.All runner converter Internal baffle 6-1 intersect at a point on right side, and the left side central point of this point and heat exchanger cylindrical shell 7 baffle plates coincides.In runner converter 6 cross sections, left side and heat exchanger, end socket 2 cross sections, right side coincide.Heat exchanger outside head 1 cross section, right side and cross section, heat exchanger cylindrical shell right side coincide.Runner converter 5, heat exchanger outside head 3, in heat exchanger, end socket 4 is respectively runner converter 6, heat exchanger outside head 1, in heat exchanger, end socket 2 is with respect to the mirror image of the central cross-section on heat exchanger left and right directions.Except heat exchanger pedestal 8 and heat exchanger pedestal 9, remaining part be all along Y-axis to axially symmetric structure.Heat exchanger pedestal 8 coincides with the upper curved surfaces of heat exchanger pedestal 9 and the outer surface of heat exchanger cylindrical shell.In said structure, except heat exchanger pedestal 8 and heat exchanger pedestal 9, remaining part in use all in axial direction rotates with speed under external force condition.
The cylindrical shell baffle number of above-mentioned heat exchanger can be more than 2 or 2 even number, and the quantity of the dividing plate of runner converter is identical with it simultaneously, and in runner converter, the quantity of outer baffle is respectively the half of above-mentioned quantity.
The area of cross section, the left side E of the runner converter of above-mentioned heat exchanger is 0.1-0.9:1 with the ratio of heat exchanger cylindrical shell left side area of section
The Internal baffle of runner converter of above-mentioned heat exchanger and the tapering of outer baffle are 10-170 degree.
Point segmental arc of the A end face circle of above-mentioned double-conical surface multiple passageway mixing unit is 0.5-2:1 for forming the segmental arc of vertebra face fin with the ratio of the corresponding central angle of segmental arc for forming vertebra face groove
Said structure is except except heat exchanger pedestal 8 and heat exchanger pedestal 9, and the speed that remainder in use rotates is vertically 0-100r/s.
Novel full adverse current of the present invention is rotated without direct contact heat exchanger, its principle is in use: cold fluid flows into from heat exchanger left side ring section A, fluid in the time touching the left-hand face of end socket 2 in heat exchanger owing to being stopped, flow into the G runner of runner converter 6 along interior end socket left-hand face, the liquid of G runner is owing to being subject to the barrier effect of heat exchanger runner converter 6 outer baffles, enter the H runner of runner converter 6, in H runner, flow through runner corresponding with H runner in heat exchanger cylindrical shell simultaneously, this fluid streams flows through the F runner that enters heat exchanger runner converter 5 after heat exchanger cylindrical shell, be subject to the effect of the outer baffle of heat exchanger runner converter 5 simultaneously, collect to center, enter the E runner of heat exchanger runner converter 5.This fluid streams flows through after runner converter 5, owing to being subject to the barrier effect of end socket 4 left-hand face in heat exchanger, collects to center, is finally flowed out by core flow outlet, heat exchanger right side D.Hot fluid flows into from heat exchanger right side ring section C, fluid in the time touching the right lateral surface of end socket 4 in heat exchanger owing to being stopped, flow into the G runner of runner converter 5 along interior end socket 4 left-hand face, the liquid of G runner is owing to being subject to the barrier effect of heat exchanger runner converter 5 outer baffles, enter the H runner of runner converter 5, in H runner, flow through runner corresponding with H runner in heat exchanger cylindrical shell simultaneously, this fluid streams flows through the F runner that enters heat exchanger runner converter 6 after heat exchanger cylindrical shell, be subject to the effect of the outer baffle of heat exchanger runner converter 6 simultaneously, collect to center, enter the E runner of heat exchanger runner converter 6.This fluid streams flows through after runner converter 6, owing to being subject to the barrier effect of end socket 2 right lateral surface in heat exchanger, collects to center, is finally flowed out by heat exchanger left side core flow outlet B.The passage of cold and hot two fluid streams in heat exchanger carries out heat exchange, and the situation of mixing can not occur in passage space.Cold fluid and hot fluid in heat exchanger in flow process, owing to being subject to the impact of heat exchanger self rotation, fluid in heat exchanger through time, its streamline be helical forward, increased the mobile distance of fluid in heat exchanger.While is due to the existence of turning effort, increase the less turbulence of fluid, upgrade the boundary layer of heat exchange, while is due to the existence of turning effort, fluid mixes the inner constantly oneself of runner, increase the temperature uniformity of fluid issuing, improved the mean temperature difference of heat exchange, reached the object of augmentation of heat transfer.
Of the present invention of many uses, can be applicable to the heat conduction reinforced or temperature homogenisation between different fluid in commercial Application.While being applied to different occasions, can select Different structural parameters.
The present invention is as a kind of new type heat exchanger, and tool has the following advantages:
1. simple in structure, it is convenient to make and install, and owing to having adopted rotational structure, reaches the required weight of metallic materials of same flow pattern and reduces, thereby reduced equipment investment;
2. full counter-flow heat exchange, has increased heat exchange mean temperature difference, has strengthened heat-transfer effect.
3. heat transfer efficiency is high, and fluid temperature (F.T.) homogenization is obvious, and the time of staying is well improved;
4. flow resistance is low, and the energy consumption that reaches identical heat-transfer effect is little;
5. continuous flow line type design, flows without dead band, and indivedual burst situations that cannot flow out blender that flow can not occur;
Pair boundary layer to peel off effect better, internal flow constantly impacts heat-transfer area, convective heat-transfer coefficient in reinforced pipe, augmentation of heat transfer;
7. cold fluid and hot fluid runner in rotary course remains released state, occurs without mixing phenomena;
8. for different application scenarios and operating condition, flexibly changing cell cube structural parameters, reach optimization.
Brief description of the drawings
Fig. 1 is overall structure schematic diagram of the present invention.
Fig. 2 is outside head 1 and outside head 3 structural representations.
Fig. 3 is interior end socket 2 and interior end socket 4 structural representations
Fig. 4 is runner converter 5 and runner converter 6 structural representations
Fig. 5 is heat exchanger cylindrical shell 7 structural representations
Fig. 6 is heat exchanger pedestal 8 and heat exchanger pedestal 9 structural representations.
In figure, the 1st, heat exchanger left side outside head, the 2nd, end socket in heat exchanger left side, the 3rd, heat exchanger right side outside head, the 4th, end socket in heat exchanger right side, the 5th, heat exchanger right side runner converter, the 6th, heat exchanger left side runner converter, 6-1 is the outer baffle of runner converter, 6-2 is the Internal baffle of runner converter, and 6-3 is the dividing plate of runner converter, the 7th, and heat exchanger cylindrical shell, the 8th, heat exchanger right side pedestal, the 9th, heat exchanger left side pedestal.A is annular fluid import cross section, heat exchanger left side, B is circular fluid issuing cross section, heat exchanger left side, C is annular fluid import cross section, heat exchanger right side, D is circular outlet, heat exchanger right side, E is the left side central cross-section of runner converter, F is to be the cross section between two runner converter dividing plates and a runner converter outer baffle, the G ring section that to be runner converter left side outside form with heat exchanger cylindrical shell, the cross section between two runner converter dividing plates of H and runner converter Internal baffle and heat exchanger cylindrical shell.
Detailed description of the invention
Below for the embodiment of the present invention aspect augmentation of heat transfer, but described full adverse current rotation without the effect of direct contact heat exchanger not only in this, explanation takes a single example.
Embodiment
The full adverse current rotation adopting is 1m without the principal length of direct contact heat exchanger, diameter is 0.4 meter, wherein heat exchanger cylindrical shell dividing plate length is 0.8 meter, runner interchanger length is 0.1 meter, heat exchanger cylindrical shell dividing plate and each runner converter dividing plate quantity are 8, and each runner converter outer baffle and Internal baffle are 4.Original paper thickness is 1mm, and material is stainless steel.Runner converter left side diameter of section is 0.3m.Test medium is air, and cold air flow is 11.3 cubes of meter per seconds, inlet temperature 300K, and the flow of hot-air is 11.3 cubes of meter per seconds, inlet temperature is 800K.Utilize Fluent fluid calculation software to simulate Calculation of Heat Transfer.The heat-transfer effect obtaining contrasts with the tubular heat exchanger under identical heat exchange area condition.Tubular heat exchanger diameter of the housing 0.4m, theme length is 1m, tubulation diameter is 0.05 meter, under identical total heat exchange area condition, contrasts: full adverse current rotation is 924W without the heat transfer power of direct contact heat exchanger, and overall heat-transfer coefficient is 4.55W/m
2k, the non-uniform temperature degree of cold fluid outlet is 22K.The heat transfer power of common tubular heat exchanger is 530W, and overall heat-transfer coefficient is 1.17W/m
2k, the non-uniform temperature degree of cold fluid outlet is 67K.As can be seen from the results, under the same conditions, compared with common tubular heat exchanger, novel full adverse current rotation has improved 74% without the heat transfer power of direct contact heat exchanger, and overall heat-transfer coefficient has improved 289%, and the unevenness of outlet temperature has also had obvious reduction.
Claims (10)
1. novel full adverse current is rotated without a direct contact heat exchanger, it is characterized in that, except heat exchanger pedestal, heat exchanger other parts are in use rotated, heat exchanger is by heat exchanger cylindrical shell, runner converter, end socket in heat exchanger, heat exchanger outside head and heat exchanger pedestal form; Realize the full adverse current of two fluid streams without mixing rotary heat exchange, reach the object that strengthens heat transfer effect.
2. heat exchanger as claimed in claim 1, it is characterized in that heat exchanger cylindrical shell is the cylindrical tube that there is more than 2 or 2 even number baffle plate an inside, cylindrical shell is evenly divided into multiple even number deciles by baffle plate, left and right sides baffle plate and middle folded cylindrical tube part thereof form a fan-shaped runner, adopt runner converter as runner conversion equipment.
3. heat exchanger as claimed in claim 1, it is characterized in that described runner converter, formed by multiple interior outer baffles and dividing plate, the quantity of runner converter dividing plate is identical with the quantity of heat exchanger inner barrel baffle plate, the quantity of interior outer baffle is respectively the half of above-mentioned quantity, the H passage of runner converter and F channel spacing are arranged, and are connected respectively with the sector channel of heat exchanger cylindrical shell.
4. heat exchanger as claimed in claim 1, is characterized in that described interior end socket entrance section and runner converter E cross section coincide.
5. heat exchanger as claimed in claim 1, is characterized in that described outside head outlet and heat exchanger cylindrical shell cylindrical cross-section coincide.
6. heat exchanger as claimed in claim 1, is characterized in that described heat exchanger pedestal top circular cross-section and heat exchanging body cylindrical shell cross section coincide.
7. heat exchanger as claimed in claim 1, is characterized in that the area of cross section, the left side E of the runner converter of heat exchanger is 0.1-0.9:1 with the ratio of heat exchanger cylindrical shell left side area of section.
8. heat exchanger as claimed in claim 1, is characterized in that the Internal baffle of runner converter of heat exchanger and the tapering of outer baffle are 10-170 degree.
9. heat exchanger as claimed in claim 1, is characterized in that point segmental arc of the A end face circle of above-mentioned double-conical surface multiple passageway mixing unit, is 0.5-2:1 for forming the segmental arc of vertebra face fin with the ratio of the corresponding central angle of segmental arc for forming vertebra face groove.
10. heat exchanger as claimed in claim 1, is characterized in that said structure is except except heat exchanger pedestal (8) and heat exchanger pedestal (9), and the speed that remainder in use rotates is vertically 0-100r/s.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410406850.1A CN104180693B (en) | 2014-08-18 | 2014-08-18 | A kind of novel full adverse current rotates without direct contact heat exchanger |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410406850.1A CN104180693B (en) | 2014-08-18 | 2014-08-18 | A kind of novel full adverse current rotates without direct contact heat exchanger |
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| CN104180693A true CN104180693A (en) | 2014-12-03 |
| CN104180693B CN104180693B (en) | 2016-01-13 |
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2163357Y (en) * | 1993-07-23 | 1994-04-27 | 陈启松 | Rotary spiral fin heat exchanger |
| CN1148429A (en) * | 1994-05-09 | 1997-04-23 | 克瓦纳尔工程有限公司 | Heat exchanger |
| US6050333A (en) * | 1997-11-10 | 2000-04-18 | Albaroudi; Homam M. | Rotary heat exchange apparatus for condensing vapor |
| CN1317680A (en) * | 2000-04-10 | 2001-10-17 | 臧宝华 | Method and equipment for gas heast exchange |
| US6938687B2 (en) * | 2002-10-03 | 2005-09-06 | Holl Technologies Company | Apparatus for transfer of heat energy between a body surface and heat transfer fluid |
-
2014
- 2014-08-18 CN CN201410406850.1A patent/CN104180693B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2163357Y (en) * | 1993-07-23 | 1994-04-27 | 陈启松 | Rotary spiral fin heat exchanger |
| CN1148429A (en) * | 1994-05-09 | 1997-04-23 | 克瓦纳尔工程有限公司 | Heat exchanger |
| US6050333A (en) * | 1997-11-10 | 2000-04-18 | Albaroudi; Homam M. | Rotary heat exchange apparatus for condensing vapor |
| CN1317680A (en) * | 2000-04-10 | 2001-10-17 | 臧宝华 | Method and equipment for gas heast exchange |
| US6938687B2 (en) * | 2002-10-03 | 2005-09-06 | Holl Technologies Company | Apparatus for transfer of heat energy between a body surface and heat transfer fluid |
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| CN104180693B (en) | 2016-01-13 |
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