CN1318817C - Heat regenerator of original surface for gas turbine - Google Patents
Heat regenerator of original surface for gas turbine Download PDFInfo
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- CN1318817C CN1318817C CNB2004100259116A CN200410025911A CN1318817C CN 1318817 C CN1318817 C CN 1318817C CN B2004100259116 A CNB2004100259116 A CN B2004100259116A CN 200410025911 A CN200410025911 A CN 200410025911A CN 1318817 C CN1318817 C CN 1318817C
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- heat exchanger
- heat
- regenerator
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
- Y02E20/18—Integrated gasification combined cycle [IGCC], e.g. combined with carbon capture and storage [CCS]
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Abstract
The present invention relates to a heat regenerator of a miniature gas turbine, particularly to an original surface heat exchanger for increasing the heat efficiency of a gas turbine. The present invention can increase the compactness and the service life of the heat regenerator. An air inlet passage and an air outlet passage are installed at the bottom right corner and the top left corner of the main body of the heat regenerator, and high pressure air flows in the main body of the heat regenerator from the air inlet passage and flows out from the air outlet passage; an air inlet and an air outlet are formed by the left frame and the right frame of a space welding heat interchange plate, and a fuel gas inlet and a fuel gas outlet are formed by the upper frame and the lower frame of the space welding heat interchange plate; fuel gas flows into the main body of the heat regenerator from the fuel gas inlet and flows out from the fuel gas outlet of the other side. The center of the heat interchange plate is provided with a heat interchange corrugated sheet which forms a parallelogram, and triangular treading down zones are positioned at the left side and the right side of the heat interchange corrugated sheet; the treading down zones are used for placing flow guide sheets, and the heat interchange plate is provided with frame strips which are used for welding and sealing. By adopting the improved corrugated plate, the flow speeds of fluid of both sides are similar, the heat interchange effects of media of both sides achieve the optimum, and the heat interchange effects are increased.
Description
Technical field
The present invention relates to a kind of regenerator of miniature gas turbine, specifically a kind of a kind of original surface heat exchanger that uses for the thermal efficiency that improves gas turbine.
Background technology
Regenerator is used in the miniature gas turbine, effectively utilizes the pressure-air that heats blower outlet from the waste heat gas of turbine outlet, thereby improves the thermal efficiency of device.The general plate type heat exchanger of being formed by the dull and stereotyped stack of parallel thin that adopts, for enhanced heat exchange and increase the rigidity of plate, on flat board, suppress ripple, the sealing strip with design between the two adjacent wave cards separates, forming a passage, flows in each passage in the cold and hot fluid compartment of terrain.A kind of split type regenerator of prior art now is described by accompanying drawing 1.
Fig. 1 (a) and (b) are depicted as the split type regenerator structural representation of prior art, wherein, the air that comes out from compressor flows to regenerator 1 along 9 from lower left circular channel 6, and the ripple heat exchanger channels of the centroclinal certain angle of flowing through is heated, and flows out from upper right side circular channel 7 to enter the combustion chamber.Combustion gas enters regenerator from regenerator side 10, carries out heat exchange with air, and the cooling back is 10 outflows from the another side.Two heat exchanger plates, 2, the 3 ripple directions that form a heat exchanger channels form an angle, and with 19 sealings of two " L " shape sealing strips, reserve the air import and export around two heat exchanger plates of air side heat exchanger channels, form air import and export passage 4,5 like this; Two heat exchanger plates outsides form combustion gas side heat exchanger channels at last lower limb with straight sealing strip 20 sealings, and both sides form combustion gas respectively and import and export passage.As seen from the figure, the regenerator of this prior art comprises the corrugated plate that is welded into integral body, two circular air ports passages up and down.
That the prior art corrugated plating adopts is the identical CC of ripple size (Cross Corrugated, staggered herringbone ripple) surface and improved CC surface, this is two kinds of enhanced heat exchange surfaces, and fluid exists secondary stream can change main flow direction when the channel flow that these surfaces form.The both sides fluid flowing passage that forms for preceding a kind of surface is identical, and the cross-sectional area of runner also is identical.
But there is following problem in present regenerator:
What adopt in the split type regenerator is CC corrugated surface and improved CC surface, mechanism from augmentation of heat transfer, but utilize secondary stream and the continuous flow direction enhanced heat exchange that changes the main flow direction fluid, with the air side is example, air is after circular passage enters regenerator, once stream and secondary flow two kinds of forms, at first enter advancing as shown in Fig. 1 (a), outlet trigonum 8, enter heat exchanger plates fuse partial parallel quadrangle district then, because the heat exchanger plates passage has certain inclination angle, 8 tops the closer to the trigonum, flow resistance is big more, and flowing velocity reduces, cause the seriously inhomogeneous of fluid flow distribution, particularly this structure makes segment fluid flow be difficult to arrive the top, trigonum, and the air regenerator top area that is difficult to flow through is carried out heat exchange with combustion gas, and also promptly this structure regenerator top exists air to be difficult to " dead band " of arrival.This situation causes that not only heat exchange is inhomogeneous, and heat exchange efficiency significantly descends, and influences the life-span of regenerator.
The regenerator of this employing corrugated surface, ripple for every heat exchanger plates trigonum 8 improves, the ripple height of heat exchanger plates trigonum is lower than fuse partial parallel quadrangle district ripple height, make two heat exchanger plates 2,3 not contact in the trigonum, though the trigonum adopts this surface can play certain guide functions, but, make the regenerator heat exchange area reduce greatly like this, reduced heat exchange efficiency.
In addition, this regenerator structure is when forming a heat exchanger channels, and two heat exchanger plates 2,3 are staggered angled on flow direction, and intersecting angle is big more, has strengthened vertically flowing of fluid, and heat exchange property is good more, but crushing is also big more simultaneously.Especially to air side, gas turbine engine systems is to be used for external work done by the pressure and temperature that improves air, and if in regenerator crushing too big, that is very disadvantageous for whole gas turbine proficiency.In fact, crushing is the key factor that influences THERMAL REGENERATOR EFFICIENCIES.Along with the increase of crushing, make the easy fouling of regenerator stop up in addition.
For the regenerator that adopts the CC surface, combustion gas side, air side cross section of fluid channel area equate, this is for the both sides volume flow when close, the heat exchange effect is better, but when big as if both sides volume flow difference, volume flow as combustion gas in miniature gas turbine and air sides differs more than 3 times, and it is bigger that flow velocity differs, and the heat exchange effect obviously descends.
In the prior art for improved CC surface, just this external waviness shape is improved, determine the air of this surface formation, the ratio of combustion gas both sides cross section of fluid channel area, determine that also how improving this surface just can make regenerator media of both sides heat exchange effect best.
Summary of the invention
Purpose of the present invention just provides a kind of gas turbine regenerator structure that cold fluid and hot fluid all can be flowed according to proper form more, improving the regenerator heat exchanger effectiveness, and improve the gas turbine shape original surface heat regenerator in compactness and regenerator service life greatly.
To achieve these goals, the invention provides a kind of shape original surface heat regenerator with flow deflector, comprise the regenerator main body, the gas inlet and outlet passage is installed in the lower right corner and the upper left corner in the regenerator main body, the regenerator main body is to be welded by some heat exchanger plates, pressure-air flows to the regenerator main body from air inlet passageway, flow out from air outlet passage, by a left side of welding heat exchanger plates at interval, left frame forms air ports, by weld at interval heat exchanger plates on, bottom frame and form combustion gas and import and export, combustion gas flows to the regenerator main body from fuel gas inlet, flow out from the opposite side gas outlet, its improvements are, heat exchanger plates divides three parts to constitute: the heat exchange corrugated plate of center parallelogram, and the triangle that is positioned at the heat exchange corrugated plate left and right sides is smashed the district, leaves around the heat exchanger plates to be used for the frame bar that welds and seal, wherein, smash the district and be used for laying flow deflector.
For regenerator water conservancy diversion district, except making fluid, abundant realization evenly enters the effect of ripple heat transfer zone, because the water diversion part area accounts for significant proportion in whole heat exchange area, for the compact efficient regenerator, we carry out enhanced heat exchange to the water conservancy diversion district.We can adopt the frame mode of CC corrugated plate, plain fin or serrated fin flow deflector of the present invention, make water conservancy diversion abundant, and pressure drop reduces, and the increase heat exchange area, effectively improve heat exchange efficiency, in addition, adopt the heat exchanger plates technology of flow deflector simple, make the regenerator structure compact more.
The present invention is for the optimum Match of considering heat exchange property and crushing of choosing of adjacent two heat exchanger plates ripple direction angles of the crossing, be chosen for 60 °, fluid produces secondary flow after entering heat exchanger channels, so not only obtain higher heat exchange efficiency, and make crushing unlikely too high, total is in light weight, and compactedness is good, has improved the service life of regenerator.
Heat exchanger plates of the present invention adopts MCC (Modified Cross Corrugated, improved staggered herringbone ripple) corrugated plating improves, be that air and combustion gas actual internal area do not wait, pressure-recovery factor and volume flow according to the air fuel gas both sides are determined, the both sides rate of flow of fluid is more or less the same, and it is best that the heat exchange effect of media of both sides reaches.
Below in conjunction with accompanying drawing specific embodiments of the invention are described in detail.Other purposes and advantage in the invention also can be embodied therein.
Description of drawings
Fig. 1 (a) is a prior art shape original surface heat regenerator overall structure schematic diagram;
Fig. 1 (b) is a prior art shape original surface heat regenerator heat exchanger plates structural representation;
Fig. 2 (a) is a band flow deflector shape original surface heat regenerator overall structure schematic diagram of the present invention;
Fig. 2 (b) is a heat exchanger plates structural representation of the present invention;
Fig. 3 (a) is the shape original surface heat regenerator part fuse decomposing schematic representation of band flow deflector of the present invention and strip of paper used for sealing;
Fig. 3 (b) is along the profile of A-A among Fig. 3 (a);
Fig. 3 (c) is along the profile of B-B among Fig. 3 (a);
Fig. 4 (a) is the structural representation that air side flow deflector of the present invention adopts the CC corrugated plate;
Fig. 4 (b) is the structural representation that combustion gas side flow deflector of the present invention adopts the CC corrugated plate;
Fig. 5 (a) is the structural representation that air side flow deflector of the present invention adopts plain fin;
Fig. 5 (b) is the structural representation that combustion gas side flow deflector of the present invention adopts plain fin;
Fig. 6 (a) is the structural representation that air side flow deflector of the present invention adopts serrated fin;
Fig. 6 (b) is the structural representation that combustion gas side flow deflector of the present invention adopts serrated fin.
The specific embodiment
Accompanying drawing is specific embodiments of the invention.
Below in conjunction with accompanying drawing particular content of the present invention is described in further detail:
Shown in Fig. 2 (a), shape original surface heat regenerator is advanced by main body 1 and air, outlet circular channel 6,7 are welded to form, main body 1 is by polylith heat exchanger plates 2,3 are welded together to form, forming air during the heat exchanger plates welding advances, outlet 4,5, air advances, export external circular channel 6,7 respectively with air intake 4, air outlet slit 5 is parallel, be welded on two diagonal angles of regenerator respectively, air flows to inlet 4 along the direction shown in 9, enter heat exchange corrugated regions 12 and then derive main body 1 through flow deflector 11 along opposite side flow deflector 11, flow out regenerator along air outlet slit 5, combustion gas enters main body 1 from the regenerator side along the direction shown in 10, flows out along opposite side 10.
When forming an air side heat exchanger channels, air import and export 4,5 is not sealed, to form a series of each autoparallel air import and export 4,5, welding corresponding gas import and export passage 6,7 on the air import and export 4,5 respectively, when gas import and export passage 6,7 is welded on main body 1, the cross section is to cut away the circle that circle lacks, the chord length that its circle lacks matches with air import and export 4,5 width respectively, and gas import and export passage 6,7 can also be selected circle, rectangle, ellipse etc. for use.
Shown in Fig. 2 (b), 2,3 fens two parts of heat exchanger plates constitute: the heat exchange corrugated plate 12,13 of center parallelogram, leg-of-mutton the smashing that is positioned at heat exchange corrugated plate 12,13 the right and lefts on the heat exchanger plates distinguishes 14, smashes district 14 and is used for laying flow deflector 11.
Regenerator welds together by the sealing strip on the frame bar, and heat exchange corrugated plating crest is support with contacting of trough in the middle of utilizing.
Shown in Fig. 3 (a), be reserved with frame around on the heat exchange corrugated plating 2, adjacent two frames form two " L " shape frame bars 19 respectively, be positioned on two diagonal angles of heat exchanger plates 2, when heat exchanger plates 2,3 welding form air duct, " L " shape sealing strip is welded heat exchanger plates 2,3 along frame bar 19, not by the section of sealing separately as air import and export 4,5, extend into CC flow deflector 11 triangular in shape at air import and export 4,5, CC corrugated plate height will match with air import and export 4,5 height dimensions, and 4,5 will keep their sizes separately during welding.Only need get final product the frame strip of paper used for sealing for regenerator main body 1 welding, the flow deflector that places triangle to smash the district only needs spot welding to fix to get final product.
In addition, frame bar 20 is left in heat exchange corrugated plating 3 upper and lower parts, and straight sealing strip has formed the combustion gas heat exchanger channels along frame bar 20 with heat exchanger plates 3,2 welding, thereby obtains fuel gas inlet 17 on the frame of side and the gas outlet 18 on the frame of another side.Place respectively along combustion gas import and export 17,18 and to be trapezoidal CC flow deflector 11.Lay CC corrugated fin 11 in the water conservancy diversion district, the direction into and out of regenerator is consistent separately with fluid for direction, and the flow deflector on two heat exchanger plates is 90 ° angle respectively.
Regenerator of processing and manufacturing, very important will have high as far as possible surface density (being the heat exchange area of unit volume) exactly, requires as far as possible in best media flow mode, increase disturbance, thereby enhanced heat exchange, for reaching this purpose, it is very important selecting the structural shape of heat exchanger plates.
Shown in Fig. 3 (b), (c), form air, fuel gas flow passage 15,16 between the corrugated plating 2,3 at interval respectively, heat exchanger plates 2 fuses partly are the corrugated platings 12 of parallelogram, waveform on the corrugated plating 12 is made up of crest 25 and trough 26, same, heat exchanger plates 3 fuses partly are the corrugated platings 13 of parallelogram, and the waveform on the corrugated plating 13 is made up of crest 23 and trough 24.When forming an air duct 15, the trough 26 on the corrugated plating 12 joins with the crest 23 on the corrugated plating 13.Relative, the crest 25 on the corrugated plating 12 joins with the trough 24 on the corrugated plating 13 and has just formed a blast tube 16.The inscribed circle 21 of trough 24 is measure-alike on crest 25 on the corrugated plating 12 and the corrugated plating 13, and crest 23 inscribed circles 22 are measure-alike on trough 26 on the same corrugated plating 12 and the corrugated plating 13.We are by regulating the radius ratio of inscribed circle 21 and 22 like this, just can obtain air duct cross section 15 areas and blast tube cross section 16 areas not on year-on-year basis.The inscribed circle 21 radius ratios of inscribed circle 22 radiuses of the trough 26 of heat exchanger plates 2 and crest 25 are the pressure ratio of air and combustion gas, and same, the inscribed circle 21 radius ratios of inscribed circle 22 radiuses of the crest 23 of heat exchanger plates 3 and trough 24 are the pressure ratio of air and combustion gas.When the welding of two or more heat exchanger plates, crest and trough extend along flow channel, and fluid flows between crest and trough, and crest and the flow channel of trough formation are determining the characteristic of media flow.
Another embodiment distributes in order to obtain suitable pressure drop, and in order to obtain dissimilar flow channels, corrugated plating can have different patterns when the assembling heat exchanger plates.In Fig. 3 (b), the trough 24 of the fuse subwave card 13 on the trough 26 of the fuse subwave card 12 on the heat exchanger plates 2 and the heat exchanger plates 3 is got the different separately degree of depth, can regulate air, blast tube area of section equally.
The trough 26 of heat exchanger plates 2 and the crest 23 of heat exchanger plates 3 join and form an air side heat exchanger channels, and air heat exchanger channels 15 is formed by the trough 26 of heat exchanger plates 2 and crest 23 staggered certain angles of heat exchanger plates 3.The trough 26 of heat exchanger plates 2 and the crest of heat exchanger plates 3 23 when heat exchanger plates is welded together, have been strengthened the intensity of regenerator because intersection has a contact point.The intersecting angle of trough 26 and crest 23 is at 45 °～75 °, and best angle is 60 °.
Regenerator combustion gas side heat exchanger channels is that the trough 24 by the crest 25 of heat exchanger plates 2 and heat exchanger plates 3 joins and forms.The crest 25 of heat exchanger plates 2 and the trough of heat exchanger plates 3 24 staggered certain angles form fuel gas flow passage 16.The crest 25 of heat exchanger plates 2 has identical height with the trough 24 of heat exchanger plates 3.When welding, adopt sealing strip to make crest 25 and trough 24 that a contact point be arranged with suitable depth.When this will be avoided air to flow in another flow channel 15,, thereby the flow channel 15,16 of both sides is deformed because have higher pressure.
Form the combustion gas heat exchanger channels by the welded seal bar, thereby obtained fuel gas inlet 17 on the frame of side and the gas outlet 18 on the frame of another side.Because of air, combustion gas two media mass flow are more or less the same, and combustion gas ejects after being done work by turbine, its pressure is only slightly high than atmospheric pressure, air is can reach 3～6bar through pressure after the compressor compresses, here we get 3.8bar, thereby atmospheric density is bigger than combustion gas density, is more or less the same in order to make the both sides flow velocity, so combustion gas turnover, mouthful bigger than the air import and export cross-sectional area that facings the wind.
In addition, an alternative embodiment of the invention is that air outlet slit 5 is bigger than air intlet 4 sizes, for the miniature gas turbine of power 100kW, air outlet slit 5 is wideer by 16% than air intlet 4 sizes, also is that the air outlet slit trigonum is bigger than air intake trigonum area.This is that pressure reduces because along with the flowing of air, air themperature raises, and density reduces, and flow velocity increases, and is more or less the same in order to make air import and export rate of flow of fluid, so increase the outlet size of air.
The very important effect of flow deflector 11 is exactly that medium is flowed evenly in heat exchanger plates, and crushing is as much as possible little, and is maximum to guarantee that pressure-air does work in turbine.We have adopted straight channel flow deflector, and crushing is little, and the flow direction of medium in flow deflector is with the import and export flow direction is consistent separately.When two media flows into from import separately respectively, their flow through paths of whole heat exchanger channels are identical for each fluid streams, also are that pressure drop is identical, and it is uneven to have avoided inner fluid passage to flow.
Shown in Fig. 4 (a) and (b), the water conservancy diversion district adopts the CC corrugated surface, the waveform that its surface is certain with the heat exchanger fin punching press, and the surface coefficient of heat transfer height has sizable superiority aspect the combination property of heat transmission resistance.
Shown in Fig. 5 (a) and (b), the water conservancy diversion district adopts plain fin, and its flow resistance coefficient is less, has higher bearing strength.
Shown in Fig. 6 (a) and (b), the water conservancy diversion district adopts serrated fin, and it can be regarded plain fin that prior art adopts as and be cut into many short and small segments, staggers certain interval mutually and the discontinuous fin that forms.This fin can carry out disturbance to gas effectively, promotes fluid to form turbulent flow, destroys the boundary layer, thereby effectively improves heat exchange efficiency.Practice shows that under the identical condition of the pressure loss, its heat transfer coefficient is higher more than 30% than plain fin.Because this heat exchange efficiency of fins height can make regenerator further compact.
The shape original surface heat regenerator of band flow deflector provided by the invention, its heat exchanger plates divides three parts to constitute: the heat exchange corrugated plate of center parallelogram, be positioned at the leg-of-mutton district that smashes that is used for laying flow deflector of each heat exchanger plates the right and left, be used for the frame bar that welds and seal all around.During the processing heat exchanger plates, it is punching press ripple in center parallelogram district, heat exchanger plates the right and left is the triangle flat plate district that reserves, because the waviness curve size of drawing is very little, air, combustion gas wing passage average equivalent diameter have only about 1.5mm, so corrugated regions is less with dull and stereotyped differentiation place, boundary line fold, the fluid flow drag effects can be ignored.Then, the flow deflector that processes is laid into dull and stereotyped district, only need spot welding to fix and get final product.Flow deflector is to lay into according to air, combustion gas import and export direction separately respectively, and the flow deflector on two heat exchanger plates is 90 ° angle.Adopt the corrugated plating regenerator of this band flow deflector, the effect of flow deflector is very tangible, both sides gas can be distributed to the heat exchanger plates core uniformly and carry out heat exchange, their flow through paths of whole heat exchanger channels are identical for each fluid streams, also be that pressure drop is identical, avoided because of uneven caused what is called " short circuit " phenomenon that flows.In addition, the fluid pressure drop of flow is very little in the water conservancy diversion district, fully realizes making fluid evenly enter the effect of ripple heat transfer zone.
Claims (6)
1. gas turbine shape original surface heat regenerator, comprise regenerator main body (1), gas inlet and outlet passage (6 is installed in the lower right corner and the upper left corner in regenerator main body (1), 7), regenerator main body (1) is by some heat exchanger plates (2,3) be welded, pressure-air flows to regenerator main body (1) from air inlet passageway (6), flow out from air outlet passage (7), by welding the left side of heat exchanger plates (2) at interval, left frame forms air ports (4,5), by weld at interval heat exchanger plates (3) on, bottom frame and form combustion gas and import and export (17,18), combustion gas flows to regenerator main body (1) from fuel gas inlet (17), flow out from opposite side gas outlet (18), it is characterized in that, heat exchanger plates (2,3) divide three parts to constitute: the heat exchange corrugated plate (12) of center parallelogram, be positioned at the leg-of-mutton district (14) that smashes of heat exchange corrugated plate (12) left and right sides of heat exchanger plates, periphery leaves and is used for the frame bar (19 that welds and seal, 20), wherein, smash district (14) and be used for laying flow deflector (11), the inscribed circle radius of the trough (26) of heat exchanger plates (2) and the inscribed circle radius ratio of crest (25) are the pressure ratio of air and combustion gas, and the inscribed circle radius of the crest (23) of heat exchanger plates (3) and the inscribed circle radius ratio of trough (24) are the pressure ratio of air and combustion gas.
2. gas turbine shape original surface heat regenerator according to claim 1 is characterized in that, described to smash district (14) be smooth plates.
3. gas turbine shape original surface heat regenerator according to claim 1, it is characterized in that, flow deflector (11) is to lay into and out of the direction of regenerator main body (1) separately along air and combustion gas into to smash district (14), and the flow deflector (11) on two heat exchanger plates (2,3) is 90 ° of angles.
4. according to claim 1 or 3 described gas turbine shape original surface heat regenerators, it is characterized in that described flow deflector (11) adopts staggered herringbone ripple CC corrugated plate or plain fin or serrated fin.
5. according to claim 1 or 3 described gas turbine shape original surface heat regenerators, it is characterized in that described flow deflector (11) is a serrated fin, this serrated fin is cut into by plain fin, stagger mutually certain interval and the row the discontinuous fin.
6. gas turbine shape original surface heat regenerator according to claim 1, it is characterized in that, described heat exchanger plates (2,3) is when connecting into heat exchanger channels, the crest (23) of going up heat exchange corrugated plate (13) at the trough (26) and the heat exchanger plates (3) of the last heat exchange corrugated plate (12) of heat exchanger plates (2) interlocks 45 °-75 ° in the ripple direction, and the corrugated plate (12,13) of two heat exchanger plates (2,3) is a contact.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2004100259116A CN1318817C (en) | 2004-03-04 | 2004-03-04 | Heat regenerator of original surface for gas turbine |
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| Application Number | Priority Date | Filing Date | Title |
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| CNB2004100259116A CN1318817C (en) | 2004-03-04 | 2004-03-04 | Heat regenerator of original surface for gas turbine |
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| CN1560437A CN1560437A (en) | 2005-01-05 |
| CN1318817C true CN1318817C (en) | 2007-05-30 |
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| CNB2004100259116A Expired - Fee Related CN1318817C (en) | 2004-03-04 | 2004-03-04 | Heat regenerator of original surface for gas turbine |
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| FR2850308B1 (en) * | 2003-01-28 | 2005-03-04 | Commissariat Energie Atomique | PERIPHERAL DEVICE FOR PRINTING AND CUTTING PAPER SHEETS USING LOW POWER LASER SOURCE |
| CN1327999C (en) * | 2005-04-11 | 2007-07-25 | 西安交通大学 | Welding cell plate and method for composing original surface regenerator core thereby |
| CN100351601C (en) * | 2005-05-23 | 2007-11-28 | 西安交通大学 | Primary surface heat exchanger for fresh air interchanger |
| CN100402815C (en) * | 2006-10-13 | 2008-07-16 | 西安交通大学 | Process for processing ring-shape original surface heat regenerator for minisize gas turbine |
| JP5733900B2 (en) * | 2010-02-26 | 2015-06-10 | 三菱電機株式会社 | Manufacturing method of plate heat exchanger and plate heat exchanger |
| CN102072022B (en) * | 2010-12-09 | 2013-12-18 | 常州大学 | Heat exchange matrix of double-wave primary surface recuperator for micro gas turbine |
| CN102654376A (en) * | 2012-04-20 | 2012-09-05 | 苏州制氧机有限责任公司 | Chamfered air extracting opening device of plate-fin type heat exchanger in main heat exchanger |
| CN103047892A (en) * | 2013-01-31 | 2013-04-17 | 天津华赛尔传热设备有限公司 | Heat transfer plate used for quadrilateral heat exchanger |
| CN104329964B (en) * | 2014-09-09 | 2016-07-06 | 北京航空航天大学 | A kind of high efficiency, low cost tubular type regenerator for miniature gas turbine |
| CN104896977A (en) * | 2015-03-09 | 2015-09-09 | 上海交通大学 | Integrated primary surface micro-channel compact heat exchanger |
| CN105571358B (en) * | 2015-12-30 | 2018-06-05 | 中国航空工业集团公司沈阳发动机设计研究所 | A kind of primary surface heat exchanger |
| US10458336B2 (en) * | 2017-02-13 | 2019-10-29 | General Electric Company | Apparatus including heat exchanger and sound attenuator for gas turbine engine |
| CN107044347B (en) * | 2017-05-23 | 2019-09-17 | 新奥能源动力科技（上海）有限公司 | A kind of regenerator and gas turbine |
| CN109057967B (en) * | 2018-06-11 | 2020-07-28 | 北京航空航天大学 | Miniature gas turbine and original surface heat regenerator |
| CN109296465A (en) * | 2018-10-21 | 2019-02-01 | 至玥腾风科技投资集团有限公司 | Regenerator, miniature gas turbine and miniature gas turbine generating set |
| CN115790216A (en) * | 2022-10-26 | 2023-03-14 | 杭州迈科瑞科技有限公司 | Primary surface heat exchanger and use method thereof |
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| CN2596035Y (en) * | 2002-12-27 | 2003-12-31 | 沈阳黎明航空发动机(集团)有限责任公司 | Mini combustion turbine heat regenerator |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN2596035Y (en) * | 2002-12-27 | 2003-12-31 | 沈阳黎明航空发动机(集团)有限责任公司 | Mini combustion turbine heat regenerator |
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