CN1318743C - Original surface heat regenerator suitable to mini type gas turbine - Google Patents
Original surface heat regenerator suitable to mini type gas turbine Download PDFInfo
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- CN1318743C CN1318743C CNB2005100427277A CN200510042727A CN1318743C CN 1318743 C CN1318743 C CN 1318743C CN B2005100427277 A CNB2005100427277 A CN B2005100427277A CN 200510042727 A CN200510042727 A CN 200510042727A CN 1318743 C CN1318743 C CN 1318743C
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Abstract
The present invention discloses a heat regenerator which is suitable for the original surface of a micro gas turbine. The air inlet outlet points of two opposite angles of the main body of the heat regenerator are provided with an air inlet pipe and an air outlet pipe. The lower part of the main body of the heat regenerator is provided with a diversion hole plate of a gas inlet. The diversion hole plate of the gas inlet is arranged in a gas intake cavity. A gas air inlet pipe is arranged in the gas intake cavity. An air flow deflector is placed in a treading region along the direction that air enters and comes out of the main body of the heat regenerator, and is divided into at least two regions which respectively use a ripple sheet structure with different density; ripples gradually change thin along the flow direction of fluid; the middle ripple plates in each regional section all use a CC ripple structure; two opposite angles with 45 degrees of a heat exchange plate are cut away along an air inlet side and an air outlet side. The present invention can make hot fluid and cold fluid both flow according to a more reasonable form and improve the heat exchange efficiency, the compactness and the service life of the heat regenerator.
Description
Technical field
The present invention relates to a kind of shape original surface heat regenerator that is applicable to miniature gas turbine, specifically a kind of a kind of original surface heat exchanger that uses in order effectively to improve the thermal efficiency of gas turbine.
Background technique
Miniature gas turbine is a kind of new work engine, adopts advanced backheat circulation usually, is made up of gas compressor, regenerator, firing chamber and combustion gas turbine.So-called backheat circulation is meant that gas turbine engine systems comes preheating blower outlet air to adopt regenerator for effectively utilizing exhaust heat, improves the thermal efficiency of device.In general, this regenerator need start with operate in temperature 500 ℃ to 800 ℃, pressure at 0.14MPa in the scope of 1.4MPa, necessary high temperature high voltage resistant, and must satisfy the requirement that miniature gas turbine is little to the efficient height of regenerator, resistance, the life-span is long, moreover, based on the requirement of gas engine compactedness, the artificer must design the volume and weight minimum, the high-efficiency compact formula regenerator that cost is minimum.
In the miniature gas turbine regenerator, widely used is plate type heat exchanger, and the heat exchange surface that adopts is the original surface form usually.Regenerator is formed by welding assembly by the series of thin corrugated sheet together, at first be between around two corrugated sheets, to form a heat exchange unit by multi-form strip of paper used for sealing welding, to organize the cold and hot fluid heat exchanger channels that the heat exchange unit welding assembly forms the space more again, prevent that hot and cold two kinds of fluids from mixing mutually.The high-pressure air of blower outlet flows through the air side passage, and the high-temperature fuel gas that the firing chamber ejects flows through the heat exchange transmission that realizes both sides with air side passage separately.
Because gas turbine is necessary high temperature resistant to the regenerator material, the requirement of high pressure, the regenerator material has developed into and has adopted thin alloy sheets, for example with the punching press of corrosion resistant plate process, pleating formation corrugated sheet, go into corrugated plate-type heat exchangers behind the parallel stack assembly welding, but stainless thermal conductivity is lower (generally at 20W/m
2* K), the heat-transfer coefficient of regenerator be improved, then wall thickness must be reduced.The common given parameter of regenerator heat supply side gas is running temperature (delivery temperature reaches 500～800 ℃), though and heat side gas is generally through the air in the atmosphere of gas compressor compression, temperature is usually less than 200 ℃.The heat of high-temperature fuel gas is directly passed to cool air through corrugated sheet, produces bigger temperature gradient in thin plate, thus the thermal distortion that in the original surface plate, produces height easily.
Because the influence of regenerator media of both sides inlet/outlet structure, cause the inhomogeneous distribution of fluid between the heat exchanger channels, the inhomogeneous distribution of this fluid reduces THERMAL REGENERATOR EFFICIENCIES, pressure drop strengthens, this influence aggravates along with the increase of regenerator number of transfer units, and moreover, the inhomogeneous distribution of fluid also may cause the phenomenon that occurs short circuit, bypass in the passage, so in efficient, compact type regenerator, the inhomogeneous distribution of fluid is a problem that can not be ignored.
In the middle of regenerator heat exchange main body, should accomplish the localized heat balancing the load as far as possible, promptly make horizontal along regenerator, the heat load of each passage reaches balance in as far as possible little scope, channel allocation should make the length of flow of each passage close substantially, should make a side liquid basic identical at each channel resistance for making uniform fluid distribution.
Introduced a kind of so split type shape original surface heat regenerator in the patent that on October 3rd, 2002, the disclosed patent No. was WO NO.02/077557: regenerator is welded to form by regenerator heat exchange main body and heated gas inlet/outlet circular pipe.That heat exchange surface adopts is CC (Cross Corrugated, staggered herringbone ripple) surface, promptly on two heat exchanging plate, stamp out ripples measure-alike but that direction is different, certain angle of interlocking during two heat exchanging plate assembly weldings, this model room forms the runner that cross section is changeable, tortuous, it can make the fluid turbulization effectively, improves heat-transfer coefficient.Two heat exchange corrugated sheets form blast tube by two straight strip of paper used for sealing welding of opposite side, form air passageways with the 3rd heat exchanging plate by two " L " types of opposite side strip of paper used for sealing again, and the rest may be inferred, and assembly welding forms whole heat exchange main body.
The patent that the disclosed patent No. was U.S.NO.2003/0226655 on December 11st, 2003 has been introduced a kind of shape original surface heat regenerator heat exchanging plate with guide plate.Heat exchanging plate adopts CW (Cross Wavy, staggered ripple) surface, and fluctuating at the fluid flow direction passage in this surface, and is 180 ° phase difference, and the change of fluid flow direction is augmentation of heat transfer greatly.When the processing rectangular heat exchanger plate, partly process the CW ripple of parallelogram earlier at the heat exchanging plate fuse, both sides reserve flat board district triangular in shape, two heat exchange corrugated sheets form blast tube by two folded strip of paper used for sealing welding of opposite side, form air passageways with the 3rd heat exchanging plate by two straight strip of paper used for sealings of opposite side again.The influence that causes for the inhomogeneous heat exchanging that reduces the fluid Flow Distribution, insert respectively in the triangle flat plate district that heat exchanging plate form to be reserved along MEDIA FLOW to guide plate, wherein combustion gas side guide plate is the corrugated sheet along combustion gas inlet/outlet cavity direction, the air side guide plate be along air inlet/outlet tube side to rectangular channel.Because fuel gas inlet side temperature will be higher than outlet temperature in heat exchanger channels, so produce high temperature deformation and the high temperature corrosion higher than outlet side at fuel gas inlet side heat exchanging plate, thereby in patent, heat exchanging plate is divided into two-part along plate import and export central shaft, a part is in the fuel gas inlet side, heat exchanging plate adopts super heat-resisting nickel stainless steel material, another part is in the gas outlet side, adopt 347 stainless steels (OCr18Ni11Nb), two-part couple together by the mode of welding along central shaft and form a complete heat exchanging plate.
But, there is following problem in the regenerator that previous patent is mentioned in two pieces of disclosed patents introducing above: process ripple on the monoblock rectangular heat exchanger plate, air is to enter regenerator by being placed in regenerator main body upper right corner pipe, at first enter the import trigonum, enter heat exchanging plate fuse partial parallel quadrilateral district then, because the heat exchanging plate passage has certain inclination angle, along with fluid away from inlet, flow resistance is big more, flowing velocity reduces, cause the seriously inhomogeneous of fluid Flow Distribution, the inhomogeneous distribution of this fluid will cause and occur short circuit phenomenon in the passage, and particularly this structure makes the very difficult top that arrives the inlet trigonum of segment fluid flow, the i.e. downstream of entrance section, cause air be difficult to flow through this zone and combustion gas to carry out heat exchange, in the middle of regenerator heat exchange main body, will exist localized heat load unbalanced.This situation causes that not only heat exchange efficiency significantly descends, and influences the life-span of regenerator.
In a back patent in order to prevent that heat exchanging plate from producing high temperature deformation and high temperature corrosion, heat exchanging plate is divided into two-part along central shaft, adopts different materials, but because corrugated sheet is very thin, fusion is difficult for guaranteeing with tightness during two-part welding, and can produce certain buckling deformation at postwelding.This not only can increase the flow resistance of fluid in passage, and the tightness can influence regenerator entire body assembly welding the time.In addition, in patent, do not mention technology contents about corrugated surface concrete form and process aspect.
Summary of the invention
Purpose of the present invention just provides a kind of gas turbine shape original surface heat regenerator, and cold fluid and hot fluid all can be flowed according to proper form more, improving the regenerator heat exchange efficiency, and improves greatly compactness and regenerator working life.
To achieve these goals, technological scheme of the present invention is achieved in that
A kind of gas turbine shape original surface heat regenerator, comprise the regenerator main body, the regenerator main body is to be formed by some unit group sheet assembly welding, each unit group sheet is welded by straight " L " type strip of paper used for sealing between two heat exchanging plate and each limit of corrugated sheet, heat exchanging plate divides two-part: the heat exchange corrugated plate of center parallelogram, be positioned at the leg-of-mutton district that smashes of the heat exchange corrugated plate left and right sides, smash the district medium advance, Way out is laid air conducting sheet and gas diversion sheet, arrange that at air ports place, two diagonal angles of regenerator main body air advances, outer pipe, fuel gas inlet water conservancy diversion orifice plate is installed in the bottom of regenerator main body, fuel gas inlet water conservancy diversion orifice plate is arranged on the combustion gas air-inlet cavity, in the combustion gas air-inlet cavity, gas inlet pipe is set, the air conducting sheet is to advance along air, the direction that goes out the regenerator main body is laid and is into smashed the district, the air conducting sheet is divided at least two sections zones, each area segments adopts the different corrugated board structures of ripple density respectively, flow direction ripple along fluid becomes thin gradually, corrugated sheet all is to adopt the CC ripple struction in each area segments, heat exchanging plate advances along air at minor face, 45 ° of two diagonal angles are cut away on the outlet limit, arrange that on these two diagonal angles air advances, outer pipe, gas diversion sheet ripple and fuel gas inlet angular separation are got 12～16 °.
The described district that smashes is after whole plate is gone out ripple, around smash and form, smash and distinguish crest and the trough mid-plane location that is positioned at heat exchanging plate.
Smash district's thickness in 0.3～0.45mm scope, smash the height that the thickness in district and the air conducting sheet of laying and gas diversion sheet thickness sum are not more than heat exchanging plate center corrugated plate.
Gas inlet pipe is made the circular cone tube, and the semi-cone angle α of circular cone tube is taken as in 3.8 °～5.4 ° the scope, and conically shaped puts in the combustion gas air-inlet cavity along fuel gas inlet, and its built-in length L optimum range is 2/5～3/5 of a regenerator length.
The heat exchanging plate center is the CW surface, the ratio of flow direction waviness curve cycle P, height H is 7, the apothem ratio of the apothem of the trough of heat exchanging plate and crest is the pressure ratio of air and combustion gas, equally, the apothem ratio of the apothem of the crest of heat exchanging plate and trough is the pressure ratio of air and combustion gas.
Circular arc plate is adopted at the base angle in the combustion gas air-inlet cavity, and circular arc plate is tangential on the base plate and the side panel in combustion gas chamber.
Circular hole on the orifice plate, more little from the near more circle hole radius of gas inlet pipe outlet, on the contrary big more.
The air intlet pipe is taper, increase along the air-flow direction bore, and in the air intlet pipe, stretch into the air inlet guide plate along import 1/5th places, guide plate extends to the inlet tube end, guide plate is divided into two-part by middle bending line, front end is even parabola, and the rear end is the rectangle that a width equals the inlet tube diameter, and the angle of front end parabola district and inlet tube center line is 10.8 °.
Regenerator heat exchanging plate of the present invention adopts CW (Cross Wavy, staggered ripple) surface, fluctuating at the fluid flow direction passage in this surface, and is 180 ° phase difference, the change of fluid flow direction is augmentation of heat transfer greatly, makes the heat exchange effect of media of both sides reach best.The heat exchanging plate structure is determined by cross-sectional direction and flow direction ripple size.
For the trigonum, be corrugating on a heat exchanging plate center parallelogram, reserve dull and stereotyped trigonum, like this because the material that adopts is a stainless steel, hardness is very big, is easy to produce fracture at ripple and dull and stereotyped watershed area, brings very big difficulty to machine shaping.Moulding of the present invention divides two-part, and the first step is all to stamp out ripple on a heat exchanging plate, and second step was that the ripple with the trigonum carries out punching press and smashes, and then laid guide plate.
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 forced heat exchanging to the water conservancy diversion district.We adopt the CC corrugated plate guide plate of the present invention, make water conservancy diversion abundant, and pressure drop reduces, and increase heat exchange area, effectively improve heat exchange efficiency.In addition, in order to save die cost, the both sides guide plate adopts identical ripple struction.
For the air intlet guide plate, because entrance section fluid upstream and downstream maldistribution will cause and occur short circuit phenomenon in the passage, in order to make fluid evenly enter the regenerator main body through guide plate along entrance section, the present invention is divided into three area segments with the import guide plate, three area segments adopt different corrugated board structures respectively, flow direction ripple along fluid becomes thin gradually, corrugated board structures is identical in each area segments, by the reallocation of adopting guide plate fluid is evenly imported the regenerator main body, to reduce the influence of maldistribution.
Air inlet/outlet and pipe join, so the inlet/outlet area is less, for increasing the inlet/outlet area, reduce the pressure loss that the air inlet/outlet causes, inlet is made angular cut, also is about to two diagonal angles of rectangular heat exchanger plate and cuts away, and the inlet/outlet pipe is welded on the otch again.
The present invention not only improves regenerator fuse heat exchanging plate, with the heat exchange efficiency of raising regenerator and the compactness of structure, it is minimum that pressure drop is reduced to, and the medium inlet road of regenerator is also improved, for preventing that fluid from causing short circuit in passage, the air intlet pipe is done tapered.
When air when inlet tube enters the regenerator fuse since medium when flowing along with the pipe range direction resistance increase, be evenly distributed when making air enter the regenerator fuse, in inlet tube, stretch into the hang plate of certain-length, form the air intake duct guide plate.
Regenerator entrance structure form plays a part crucial to inner assignment of traffic, on the inlet of regenerator core body heads on, for making fluid distribution even as much as possible, when combustion gas in the present invention enters the regenerator main body by the combustion gas air-inlet cavity, settle a rectangle orifice plate at fuel gas inlet pipe and core body inlet between head-on, get the circular hole of different radii on the plate according to the fuel gas flow allocation situation, combustion gas enters the combustion gas chamber from the import pipe, and then the effect by orifice plate realizes reallocation, enters the regenerator main body equably.On the other hand, add orifice plate and can avoid producing local high speed flow district in fuel gas inlet pipe outlet, and the pressure drop that fuel gas inlet is produced to account for the ratio of overall flow resistance as far as possible little.By the measure of reallocation in the middle of adopting, to reduce the influence of maldistribution.
The present invention adopts circular arc plate with base angle in the combustion gas air-inlet cavity, replace two flat boards of rectangular cavity, circular arc plate is tangential on the bottom and the sidewall in combustion gas chamber, and its purpose is to make the full and uniform regenerator main body that enters of combustion gas to carry out heat exchange, avoid at formation eddy current dead angle, base angle, thereby reduce flow resistance.
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 band guide plate shape original surface heat regenerator overall structure schematic representation of the present invention;
Fig. 1 (b) is along the B-B sectional drawing among Fig. 1 (a);
Fig. 2 (a) is a heat exchanging plate structural representation on the CW of the present invention surface;
Fig. 2 (b) is a local I enlarged diagram among Fig. 2 (a);
Fig. 2 (c) is along the sectional drawing of C-C among Fig. 2 (a);
Fig. 3 (a) is a heat exchanging plate structural representation under the CW of the present invention surface;
Fig. 3 (b) is a local I I enlarged diagram among Fig. 3 (a);
Fig. 3 (c) is along the sectional drawing of D-D among Fig. 3 (a);
Fig. 4 (a) is the structural representation that combustion gas side guide plate of the present invention adopts the CC surface;
Fig. 4 (b) is the structural representation that air side guide plate of the present invention adopts the CC surface;
Fig. 4 (c) is that Fig. 4 (a) and (b) are respectively along the schematic representation of E, F direction;
Fig. 5 is that the present invention improves back air inlet guide plate region division schematic representation;
Fig. 6 is a fuel gas inlet pod apertures plate structure schematic representation of the present invention;
Fig. 7 (a) is an air intlet tubular construction schematic representation of the present invention;
Fig. 7 (b) is a deflector structure schematic representation in the air intlet pipe of the present invention.
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. 1 (a), shape original surface heat regenerator is by regenerator main body 1, circular channel air inlet/ outlet pipe 6,7, and gas inlet pipe 10, combustion gas air-inlet cavity 11 and combustion gas air inlet water conservancy diversion orifice plate 12 are welded to form.The regenerator main body is by some heat exchanging plate 2,3 are welded, form air inlet/ outlet 4,5 during the heat exchanging plate welding, air inlet/ outlet 4,5 external circular channels, air inlet/ outlet pipe 6,7 is parallel with air intlet 4, air outlet slit 5 respectively, be welded on two diagonal angles of regenerator respectively, air flows to air intlet 4 from air intlet pipe 6, enter heat exchange corrugated plate 18 through air conducting sheet 13, and then 5 enter air outlet slit pipe 7 from the opposite side guide plate along air outlet slit, derive regenerator main body 1, flow out regenerator.Combustion gas flows to rectangle combustion gas air-inlet cavity 11 from fuel gas inlet pipe 10, enter regenerator main body 1 by 12 distribution of fuel gas inlet water conservancy diversion orifice plate, enter heat exchanging plate center corrugated plate 19 from regenerator main body 1 fuel gas inlet 8 through gas diversion sheet 14 and carry out abundant heat exchange, and then flow out regenerator from opposite side guide plate gas outlet 9.
Central Plains of the present invention surface heat exchanger core body is that regenerator main body 1 is formed by some unit group sheet 20 assembly weldings, each unit group sheet 20 is by the square corrugated heat exchanging plate 2 of two lengths of a film, 3 and straight " L " type strip of paper used for sealing 16 of being inserted between each limit of corrugated sheet be welded, welded structure is: smash straight " L " type strip of paper used for sealing 16+ of district 15+ and smash district 15, between two corrugated sheets, form air flow passage, each unit group sheet 20 has an air inlet 4 and air air outlet 5 that is communicated with air flow passage, advances along air, Way out 15 is laid air conducting sheet 13 smashing the district respectively.Between each unit group sheet 20, form blast tube with pleating strip of paper used for sealing 17 welding of inserting, combustion gas enters regenerator main body 1 from fuel gas inlet 8 and carries out heat exchange, flow out regenerators from opposite side gas outlet 9, lay gas diversion sheet 14 smashing district 15 respectively along combustion gas inlet/outlet direction equally.
One embodiment of the present of invention, two ripple heat exchanging plate 2,3, corrugated regions heat exchange corrugated plate 18,19 ripple flow directions are 180 ° phase difference, and a heat exchange unit group sheet 20 by Stamping Steel Ribbon welding all around forms forms air, fuel gas flow passage at interval respectively.It is all to stamp out ripple on monolithic heat exchange flat board that heat exchanging plate 2,3 moulding divide two-part first step, and second step was that the ripple with the trigonum carries out punching press and smashes, and then laid guide plate.
The gas diversion sheet of laying in smashing district 15 respectively 13,14 adopts the CC corrugated sheets, and the abundant water conservancy diversion that makes fluid pass through guide plate enters the fuse corrugated regions and carries out abundant heat exchange, reaches thermal equilibrium.In order to save die cost, both sides gas diversion sheet 13,14 adopts identical ripple struction.In addition, the CC corrugated sheet has certain bearing capacity. Gas diversion sheet 13,14 adopts straight passage at flow direction, and crushing is little.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.
When forming an air side heat exchanger channels, for increasing the inlet/outlet area, reduce the pressure loss that the air inlet/outlet causes, inlet is made angular cut, also being about to 2,3 two diagonal angles of rectangular heat exchanger plate cuts away, weld two heat exchanging plate and will form a series of each autoparallel air inlet/ outlet 4,5 at 2,3 o'clock, be about to two diagonal angles that air inlet/ outlet 4,5 is arranged in regenerator main body 1.
Welding corresponding air inlet/ outlet pipe 6,7 on the air inlet/ outlet 4,5 respectively, when air inlet/ outlet pipe 6,7 is welded on regenerator 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 inlet/ outlet 4,5 width respectively, and air inlet/ outlet pipe 6,7 can also be selected circle, ellipse etc. for use.
Shown in Fig. 1 (b), be that gas inlet pipe 10 is made the circular cone tube, the semi-cone angle α of circular cone tube directly influences combustion gas and imports and exports tube voltage drop.The circular cone barrel structure is optimized design, and semi-cone angle α scope is taken at 3.8 °～5.4 °.In addition, the circular cone tube puts in combustion gas air-inlet cavity 11 certain-lengths, and extended length influences distribution situation and the pressure drop that combustion gas enters regenerator main body 1, so circular cone tube built-in length optimum range is 2/5～3/5 of a regenerator length.
Shown in Fig. 2 (a), 2 fens two-part of last heat exchanging plate constitute: the heat exchange center corrugated plate 18 of center parallelogram, be positioned at the leg-of-mutton district 15 that smashes of heat exchange center corrugated plate 18 the right and lefts on the heat exchanging plate, smash district 15 and be used for laying air conducting sheet 13.Smashing district's moulding of 15 and divide two-part, at first is all to stamp out ripple on heat exchanging plate 2, is that ripple with the trigonum carries out punching press and smashes then.The thickness of smashing district 15 is approximately about 3 times of original heat exchanging plate thickness, account for 1/5 of heat exchange center corrugated plate 18 height, 15 lay air conducting sheet 13 smashing the district, the thickness of smashing district 15 and the air conducting sheet 13 thickness sums of laying are not more than the height of heat exchanging plate center corrugated plate 18.
One embodiment of the present of invention for the heat exchange effect that makes media of both sides reaches best, obtain suitable pressure drop and distribute, heat exchange surface adopts the CW original surface, fluctuating at the fluid flow direction passage in this surface, and is 180 ° phase difference, and the change of fluid flow direction is augmentation of heat transfer greatly.This structure is determined by heat exchanging plate cross-sectional direction and flow direction ripple size.
As Fig. 2 (b) is CW original surface flow direction ripple schematic representation, and flow direction becomes waviness curve, from the mechanism of augmentation of heat transfer, utilizes secondary flow and constantly changes main flow direction and come augmentation of heat transfer.Waviness curve cycle P on the flow direction, the ratio of height H influence the pressure loss and the heat exchange efficiency that fluid flows.The value of P/H is bigger than normal, and heat exchange efficiency reduces; The value of P/H is less than normal, and it is big that the pressure loss becomes.So P/H optimum value of the present invention is taken as 7.
Fig. 2 (c) is the ripple schematic representation of CW original surface cross-sectional direction, air and combustion gas actual internal area do not wait, pressure-recovery factor and volume flowrate 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.Waveform on the heat exchanging plate center corrugated plate 18 is made up of crest 24 and trough 26, and incircle 25 radius size of crest 24 have determined air passageways 21 section area, and incircle 27 radius size of trough 26 have determined blast tube 22 section area.The incircle 25 radius ratios of incircle 27 radiuses of the trough 26 of heat exchanging plate 2 and crest 24 are the pressure ratio of air and combustion gas, when the welding of two or more heat exchanging plate, crest and trough extend along flow channel, fluid flows between crest and trough, and the flow channel that crest and trough form is determining the characteristic of media flow.
Shown in Fig. 3 (a), 3 fens two-part of following heat exchanging plate constitute: the heat exchange center corrugated plate 19 of center parallelogram, leg-of-mutton the smashing that is positioned at heat exchange center corrugated plate 19 the right and lefts on the heat exchanging plate distinguishes 15, smashes district 15 and is used for laying guide plate.Smash the method for same Fig. 2 of moulding (a) introduction in district 15, repeat no more here.
As Fig. 3 (b) is CW original surface flow direction ripple schematic representation in the following heat exchanging plate 3, the structure of being introduced among same Fig. 2 of waviness curve (b).
Fig. 3 (c) is following heat exchanging plate 3 cross section ripple schematic representation, waveform on the heat exchange center corrugated plate 19 is made up of crest 28 and trough 30, incircle 29 radius size of crest 28 have determined blast tube 22 section area, and incircle 31 radius size of trough 30 have determined air passageways 21 section area.The incircle 31 radius ratios of incircle 29 radiuses of the crest 28 of heat exchanging plate 3 and trough 30 are the pressure ratio of air and combustion gas.
When forming an air passageways 21, the trough 26 on the heat exchange center corrugated plate 18 joins with the crest 28 on the heat exchange center corrugated plate 19.Relative, the crest 24 on the heat exchange center corrugated plate 18 joins with the trough 30 on the heat exchange center corrugated plate 19 and has just formed a blast tube 22.The incircle 31 of trough 30 is measure-alike on the incircle 25 of the crest 24 on the heat exchange center corrugated plate 18 and the heat exchange center corrugated plate 19, and crest 28 incircles 29 are measure-alike on the incircle 27 of the trough 26 on the same heat exchange center corrugated plate 18 and the heat exchange center corrugated plate 19.We are by regulating the radius ratio of incircle 25 and 27 like this, just can obtain air passageways cross section 21 areas and blast tube cross section 22 areas not on year-on-year basis.Regenerator welds together by the Stamping Steel Ribbon on the frame bar, and heat exchange corrugated sheet crest is support with contacting of trough in the middle of utilizing.
Shown in Fig. 4 (a), gas diversion sheet 14 adopts and is trapezoidal CC corrugated surface, and this surface is at thin plate upper punch corrugating.In order further to strengthen the heat exchange of combustion gas in the water conservancy diversion district, ripple direction and combustion gas inlet/outlet direction have certain angle, and angle is big more, and resistance is big more, and heat exchange strengthens, so gas diversion sheet 14 ripple directions and combustion gas airintake direction angle are got 12～16 °.
Shown in Fig. 4 (b), air conducting sheet 13 adopts the same CC of employing corrugated sheet, and the flow direction of air in guide plate 13 is consistent with its inlet/outlet flow direction.
Fig. 4 (c) is combustion, air conducting sheet 14,13 surface C C ripple schematic representation, the ripple height is by regenerator fuse heat exchanging plate ripple height and smash district's thickness decision, its flow resistance coefficient is less, has certain bearing strength, can make whole regenerator structure compact more.
An alternative embodiment of the invention is that the air inlet guide plate is divided into several zone sections, the definite of zone hop count can adjust according to the length of regenerator, divide the corresponding increase die cost of more more meetings, with reference to Fig. 5, the air inlet guide plate is divided into three area segments I, II, III, each area segments adopts the different corrugated board structures of ripple density respectively, flow direction ripple along fluid becomes thin gradually, corrugated sheet all is to adopt the CC ripple struction in each area segments, fluid evenly imports regenerator regenerator main body 1 by the reallocation of adopting air conducting sheet 13, to reduce the influence of maldistribution.Regenerator entrance structure form plays a part crucial to inner assignment of traffic, by this intake method, can make heat transferring medium enter exchanging air equably, avoid because entrance section fluid upstream and downstream maldistribution will cause and occur short circuit phenomenon in the passage.
An alternative embodiment of the invention is to settle fuel gas inlet water conservancy diversion orifice plate 12 in combustion gas air-inlet cavity 11, with reference to Fig. 1 and Fig. 6 when combustion gas enters regenerator main body 1 by combustion gas air-inlet cavity 11, between gas inlet pipe 10 and fuel gas inlet 8, settle a rectangle fuel gas inlet water conservancy diversion orifice plate 12, get the circular hole of different radii on the fuel gas inlet water conservancy diversion orifice plate 12 according to the fuel gas flow allocation situation, combustion gas enters combustion gas chamber 11 from suction tude 10, and then the effect by fuel gas inlet water conservancy diversion orifice plate 12 realizes reallocation, enters regenerator main body 1 equably.On the other hand, add fuel gas inlet water conservancy diversion orifice plate 12 and can avoid producing local high speed flow district in fuel gas inlet pipe outlet, and the pressure drop that fuel gas inlet is produced to account for the ratio of overall flow resistance as far as possible little.The open-cellular form of fuel gas inlet water conservancy diversion orifice plate 12 can be determined by combustion gas pneumatic design result of calculation according to the semi-cone angle α of gas inlet pipe 10 and the degree of depth difference that stretches into combustion gas air-inlet cavity 11.
Make pipe with reference to air intlet pipe 6 shown in Fig. 7 (a), in inlet tube, stretch into the inclination air inlet guide plate 32 of certain-length, its purpose is evenly distributed when being to make air to enter the regenerator fuse, avoids forming one " dead angle " at tube end, causes the media of both sides heat exchange inhomogeneous.
Fig. 7 (b) is that air inlet guide plate 32 launches schematic representation, and guide plate 32 is divided into two-part by middle bending line, and front end is even parabola, and the rear end is the rectangle that a width equals suction tude 6 diameters.The angle of front end parabola district and suction tude 6 center lines is 10.8 °.
More than by embodiment the present invention is described in detail, those skilled in the art should be understood that embodiment only is an exemplary forms.Can carry out various changes and modifications when the present invention is used according to actual state, these distortion and revise all should drop within the claim scope that the inventor advocates.
Claims (8)
1. gas turbine shape original surface heat regenerator, comprise regenerator main body (1), regenerator main body (1) is formed by unit group sheet (20) assembly welding, each unit group sheet (20) is by two heat exchanging plate (2,3) and straight " L " type strip of paper used for sealing (16) between each limit of corrugated sheet be welded, heat exchanging plate (2,3) divide two-part: the heat exchange corrugated plate (18 of center parallelogram, 19), and be positioned at heat exchange corrugated plate (18,19) the leg-of-mutton district (15) that smashes of the left and right sides, advance smashing district (15) medium, Way out is laid air conducting sheet (13) and gas diversion sheet (14), in (1) two diagonal angle air ports (4 of regenerator main body, 5) locate to arrange that air advances, outer pipe (6,7), it is characterized in that, in the bottom of regenerator main body (1) fuel gas inlet water conservancy diversion orifice plate (12) is installed, fuel gas inlet water conservancy diversion orifice plate (12) is arranged on the combustion gas air-inlet cavity (11), gas inlet pipe (10) is set in combustion gas air-inlet cavity (11), air conducting sheet (13) advances along air, the direction that goes out regenerator main body (1) is laid and is into smashed district (15), air conducting sheet (13) is divided at least two sections zones, each area segments adopts the different corrugated board structures of ripple density respectively, flow direction ripple along fluid becomes thin gradually, corrugated sheet all is to adopt the CC ripple struction in each area segments, heat exchanging plate (2,3) advance along air at minor face, 45 ° of two diagonal angles are cut away on the outlet limit, and gas diversion sheet (14) ripple and fuel gas inlet angular separation are got 12～16 °.
2. gas turbine shape original surface heat regenerator according to claim 1 is characterized in that, the described district (15) that smashes is after whole plate is gone out ripple, around smash and form, smash crest and trough mid-plane location that district (15) is positioned at heat exchanging plate (2,3).
3. gas turbine shape original surface heat regenerator according to claim 1 and 2, it is characterized in that, smash district (15) thickness in 0.3～0.45mm scope, smash the height that the thickness in district (15) and the air conducting sheet of laying (13) and gas diversion sheet (14) thickness sum are not more than heat exchanging plate center corrugated plate (18,19).
4. gas turbine shape original surface heat regenerator according to claim 1, it is characterized in that, gas inlet pipe (10) is made the circular cone tube, the semi-cone angle α of circular cone tube is taken as in 3.8 °～5.4 ° the scope, conically shaped puts in combustion gas air-inlet cavity (11) along fuel gas inlet, and its built-in length L scope is 2/5～3/5 of a regenerator length.
5. gas turbine shape original surface heat regenerator according to claim 1, it is characterized in that, heat exchanging plate (2,3) center is the CW surface, the ratio of flow direction waviness curve cycle P, height H is 7, incircle (25) the radius ratio of incircle (27) radius of the trough (26) of heat exchanging plate (2) and crest (24) is the pressure ratio of air and combustion gas, equally, incircle (31) the radius ratio of incircle (29) radius of the crest (28) of heat exchanging plate (3) and trough (30) is the pressure ratio of air and combustion gas.
6. gas turbine shape original surface heat regenerator according to claim 1 is characterized in that, circular arc plate (23) is adopted at the interior base angle of combustion gas air-inlet cavity (11), and circular arc plate (23) is tangential on the base plate and the side panel in combustion gas chamber (11).
7. gas turbine shape original surface heat regenerator according to claim 1 is characterized in that, the circular hole on the orifice plate (12) is more little from the near more circle hole radius of gas inlet pipe (10) outlet, otherwise big more.
8. gas turbine shape original surface heat regenerator according to claim 1, it is characterized in that, air intlet pipe (6) is taper, increase along the air-flow direction bore, and in air intlet pipe (6), stretch into air inlet guide plate (32) along import 1/5th places, guide plate (32) extends to inlet tube (6) end, guide plate (32) is divided into two-part by middle bending line, front end is even parabola, the rear end is the rectangle that a width equals inlet tube (6) diameter, and the angle of front end parabola district and inlet tube (6) center line is 10.8 °.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100427277A CN1318743C (en) | 2005-05-26 | 2005-05-26 | Original surface heat regenerator suitable to mini type gas turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100427277A CN1318743C (en) | 2005-05-26 | 2005-05-26 | Original surface heat regenerator suitable to mini type gas turbine |
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| CN1696482A CN1696482A (en) | 2005-11-16 |
| CN1318743C true CN1318743C (en) | 2007-05-30 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005100427277A Expired - Fee Related CN1318743C (en) | 2005-05-26 | 2005-05-26 | Original surface heat regenerator suitable to mini type gas turbine |
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| CN (1) | CN1318743C (en) |
Families Citing this family (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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 |
| CN102072023A (en) * | 2010-12-07 | 2011-05-25 | 四川达宇特种车辆制造厂 | Primary surface type regenerator |
| CN102562308B (en) * | 2011-12-15 | 2015-09-23 | 西安远航真空钎焊技术有限公司 | A kind of small efficient heat regenerator and manufacture method thereof |
| CN104246177A (en) * | 2012-02-21 | 2014-12-24 | 巴布科克·博西格·施泰因米勒有限公司 | Micro gas turbine system with a pipe-shaped recuperator |
| CN104896977A (en) * | 2015-03-09 | 2015-09-09 | 上海交通大学 | Integrated primary surface micro-channel compact heat exchanger |
| CN109057967B (en) * | 2018-06-11 | 2020-07-28 | 北京航空航天大学 | Miniature gas turbine and original surface heat regenerator |
| CN108979864A (en) * | 2018-08-08 | 2018-12-11 | 北京航空航天大学 | A kind of miniature gas turbine and regenerator |
| CN109057968A (en) * | 2018-10-21 | 2018-12-21 | 至玥腾风科技投资集团有限公司 | Miniature gas turbine generating set |
| 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 |
| CN112709636A (en) * | 2019-10-25 | 2021-04-27 | 成都皮克电源有限公司 | Gas turbine generator set and power generation process |
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| US4720969A (en) * | 1981-10-15 | 1988-01-26 | The United States Of America As Represented By The United States Department Of Energy | Regenerator cross arm seal assembly |
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| JP2002129979A (en) * | 2000-10-20 | 2002-05-09 | Mitsubishi Heavy Ind Ltd | Regenerator for gas turbine |
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| CN1566619A (en) * | 2003-07-04 | 2005-01-19 | 中国科学院工程热物理研究所 | Heat regenerator for small combustion turbine |
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Patent Citations (5)
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|---|---|---|---|---|
| US4720969A (en) * | 1981-10-15 | 1988-01-26 | The United States Of America As Represented By The United States Department Of Energy | Regenerator cross arm seal assembly |
| CN1086581A (en) * | 1992-11-03 | 1994-05-11 | 程大酉 | Improved backheat Composite Double fluid thermal in parallel machine |
| JP2002129979A (en) * | 2000-10-20 | 2002-05-09 | Mitsubishi Heavy Ind Ltd | Regenerator for gas turbine |
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| CN1566619A (en) * | 2003-07-04 | 2005-01-19 | 中国科学院工程热物理研究所 | Heat regenerator for small combustion turbine |
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| CN1696482A (en) | 2005-11-16 |
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