CN101050714A - Medium cooling isobaric heat sucking type air turbine - Google Patents
Medium cooling isobaric heat sucking type air turbine Download PDFInfo
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- CN101050714A CN101050714A CNA2007100974047A CN200710097404A CN101050714A CN 101050714 A CN101050714 A CN 101050714A CN A2007100974047 A CNA2007100974047 A CN A2007100974047A CN 200710097404 A CN200710097404 A CN 200710097404A CN 101050714 A CN101050714 A CN 101050714A
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- 238000001816 cooling Methods 0.000 title claims description 36
- 238000010521 absorption reaction Methods 0.000 claims abstract description 27
- 238000009423 ventilation Methods 0.000 claims description 15
- 230000008676 import Effects 0.000 claims description 14
- 239000000446 fuel Substances 0.000 claims description 12
- 238000005273 aeration Methods 0.000 claims description 9
- 230000005855 radiation Effects 0.000 claims description 9
- 230000007306 turnover Effects 0.000 claims description 8
- 238000010304 firing Methods 0.000 claims description 7
- 230000003534 oscillatory effect Effects 0.000 claims description 7
- 238000009434 installation Methods 0.000 claims description 5
- 230000005540 biological transmission Effects 0.000 claims description 4
- 238000010992 reflux Methods 0.000 claims description 4
- 239000002826 coolant Substances 0.000 claims description 3
- 238000013022 venting Methods 0.000 claims description 3
- 238000000034 method Methods 0.000 abstract description 22
- 239000007789 gas Substances 0.000 description 57
- 238000007906 compression Methods 0.000 description 20
- 230000008569 process Effects 0.000 description 18
- 230000006835 compression Effects 0.000 description 16
- 238000002485 combustion reaction Methods 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 5
- 230000007246 mechanism Effects 0.000 description 5
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 4
- 239000000567 combustion gas Substances 0.000 description 4
- 230000009467 reduction Effects 0.000 description 4
- 125000004122 cyclic group Chemical group 0.000 description 3
- 238000000605 extraction Methods 0.000 description 3
- 230000009183 running Effects 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000002411 adverse Effects 0.000 description 2
- 229910002092 carbon dioxide Inorganic materials 0.000 description 2
- 239000001569 carbon dioxide Substances 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 239000005431 greenhouse gas Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 206010048669 Terminal state Diseases 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 238000004458 analytical method Methods 0.000 description 1
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- 238000007599 discharging Methods 0.000 description 1
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- 230000002349 favourable effect Effects 0.000 description 1
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- 239000013535 sea water Substances 0.000 description 1
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- 239000004449 solid propellant Substances 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/12—Cooling of plants
- F02C7/16—Cooling of plants characterised by cooling medium
- F02C7/18—Cooling of plants characterised by cooling medium the medium being gaseous, e.g. air
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
- F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The present invention provides an intercooling equipressure heat-of-absorption type air turbine. It includes the following several portions: intercooler, heater, boiler, air compressor and air turbine connected with main shaft. Said invention also provides its working principle and its concrete operation method.
Description
Technical field the present invention relates to a kind of air turbine, particularly relates to a kind of cooling isobaric heat sucking type air turbine that is used for power plant.
The steam power plant characteristics high-power with it and reliable operation that background technique is made of boiler, steam turbine and condenser are widely used in the power plant of power plant's generating.But in steam power plant, carry out condensation in the condenser and be transformed into water again because of exhaust steam after the work done that goes out steam turbine will enter, a large amount of latent heat in the exhaust steam are loose has produced very big radiation loss to the external world.And application number be " 200710086603.8 " described in the cooling isobaric heat sucking type heat engine, though cool off isobaric heat absorption and utilize air to avoid the vapor condensation loss in the vapor recycle as working medium by the centre, but because middle cooling isobaric heat sucking type heat engine is a kind of motor that utilizes piston to carry out work done, when making more powerful power plant, power conversion mechanism in the form of piston obviously can keep less size and volume like that not as steam turbine.
Summary of the invention the objective of the invention is on the core isobaric heat absorption architecture basics of cooling isobaric heat sucking type heat engine in reservation, provide a kind of middle cooling isobaric heat sucking type air turbine in conjunction with this impeller power conversion mechanism of gas-turbine, this air turbine not only has very high heat absorption utilization ratio, but also, generate electricity thereby make it be more suitable for being used for power plant because of adopting gas-turbine to can be made into more powerful power plant.
Cooling isobaric heat sucking type air turbine comprises interstage cooler, heater, boiler, gas compressor and the gas-turbine that links to each other through main shaft in of the present invention, and heater is located in the boiler, perhaps is located in the high-temperature exhaust air or Drainage pipe of other thermal source.It is characterized in that: it also comprises several air distributing devices that rotary cylinder-block constituted by shell and Qi Nei, on the central shaft that rotary cylinder-block is contained in shell is fixedlyed connected, be respectively equipped with on it around the little secondary cylinder of the band cold aeration mouth of central shaft annular array and first mate's cylinder of the hot ventilating hole of opposite side band, corresponding big or small gas distribution piston links to each other with turnover swash plate transmission on the central shaft by connecting rod in first mate's cylinder and the little secondary cylinder, and rotary cylinder-block is driven by the central gear on the main shaft through the gear on it; When rotary cylinder-block rotates, cold aeration mouth on the little secondary cylinder can be respectively with the little valve disc of shell side on set inflation inlet and take a breath and link up mutually, the hot ventilating hole on first mate's cylinder can be respectively with the big valve disc of shell opposite side on set ventilation import and air outlet link up mutually; The inflation inlet of the outlet passageway of described gas compressor on the little valve disc of interstage cooler and air distributing device is connected, the ventilation of little valve disc outlet by the road, heater and heat insulating tube be connected with ventilation import on the big valve disc, and the suction port of gas-turbine is led in the air outlet of valve disc through the pressure heat insulating tube greatly; When adopting boiler to make external heat source, interstage cooler is located in the cooling air jacket with the reflux type heat exchange, and the pipeline of heat radiation air outlet slit through being provided with blower of coolant jacket leads to the corresponding intake grill of boiler.
For allowing big or small gas distribution piston adopt stronger drive mechanism, in described air distributing device, each big gas distribution piston in the rotary cylinder-block is connected as a single entity through tie-beam and corresponding little gas distribution piston respectively, the inboard of tie-beam has the recessed portion of avoiding the turnover swash plate, on the outer side surface of tie-beam, be provided with slide rail, on the inner side surface opposite position of rotary cylinder-block connection shell, be provided with a rail, the roller row who constitutes with retainer and roller is housed between present rail and the slide rail; Be provided with the single installation shaft of several double or intermediate arrangement of arranging in both sides on retainer, identical intermediate gear is housed on the axle, respective rack set on these gears and a rail and the slide rail is meshed.
In the concrete layout of air distributing device, can allow described air distributing device around main shaft symmetry or ring-like layout, the air outlet on it is relative with the suction port of gas-turbine and be communicated with through the pressure heat insulating tube.Also can establish one group of identical air distributing device again in the outside of the symmetry or the air distributing device of ring-like layout, the angle that the air distributing device of this assembly device of air and inboard staggers certain is installed, allow each corresponding air outlet on it respectively through pass inboard air distributing device at interval the lengthening pressure heat insulating tube in space lead to the suction port of gas-turbine, the main shaft of lengthening drives the gear on the rotary cylinder-block in the air distributing device by the central gear in the outside.
In the air turbine that adopts closed cycle, gas compressor is located at the rear portion of gas-turbine, the import positioned opposite of the relief opening of gas-turbine and gas compressor, be communicated with by being communicated with the letter road between two gas ports, be provided with air preheater in being communicated with the letter road, the pipeline of the exhaust port of preheater through being provided with blower leads to the corresponding intake grill of boiler.
For being located at the concrete structure that is communicated with air preheater in the letter road, set air preheater is made of the heat absorption flat tube of some quantity, these heat absorption flat tubes have suitable long length and in-line arrangement air-flow in the connection letter road that is located at the annular table, each flat tube that absorbs heat is radial with its cross section and arranges in annular is communicated with the letter road, some the endothermic plates of being arranged by downstream direction between each adjacent heat absorption flat tube link to each other, the continuous whole preheater structure that constituted an annular of each flat tube that absorbs heat by endothermic plate, the turning point front end and the afterbody of each flat tube that absorbs heat are streamline shape.
In the air turbine that adopts open cycle, the corresponding intake grill of boiler is led in the exhaust passage of gas-turbine, the venting valve of opening when being provided with low-power on the exhaust passage.
For reclaiming the heat in the gas-turbine exhaust, the relief opening of gas-turbine leads to the external world through the exhaust passage that is provided with air preheater, and the pipeline of the exhaust port of air preheater through being provided with blower leads to the corresponding intake grill of boiler.
For allowing the Air wheel function increase transmission power in the internal combustion mode, be provided with the bypass line of band firing chamber in the periphery of the pressure heat insulating tube that is connected with the air distributing device air outlet, between the import of bypass line and pressure heat insulating tube, be provided with oscillatory valve, when burn in the firing chamber, oscillatory valve swings in the pressure heat insulating tube accordingly from cutting out the bypass line position.Certainly, also can adopt simpler combustion chamber placement mode, with pressure heat insulating tube that the air distributing device air outlet is connected on directly be provided with tail pipe burner, set telescopic fuel injector can put in tail pipe burner when burner oil.
Cooling isobaric heat sucking type air machine in of the present invention is owing to grow up on the isobaric heat absorption core texture basis in the cooling isobaric heat sucking type heat engine in reservation, this power plant still have the highest heat absorption efficiency, can exhaust the heat of high temperature gas flow in the external heat source substantially.When air turbine of the present invention adopts boiler as external heat source, participate in burning owing to can introduce boiler to the heat radiation air of interstage cooler, make the compression heat that produces in the gas compressor also can be recovered sharp amount, thereby increased substantially the thermal efficiency of this external-burning type air turbine of the present invention.Has the highest thermal efficiency of cycle, simultaneously also can allow gas-turbine send very big power, these advantages make air turbine of the present invention be particularly suitable for power plant and generate electricity, thereby for the fuel consumptions and the reduction discharge of carbon dioxide greenhouse gas of minimizing power plant have been created condition in a large number.
In addition, in air turbine of the present invention, through carrying out perfect to the driving mechanism that gas distribution piston adopted in the air distributing device, allow the tie-beam between the big or small gas distribution piston contact by the seat rail that roller row is connected with rotary cylinder-block on the shell, big or small gas distribution piston and tie-beam are being born under the very big centrifugal action, also can not produce too big surface friction drag and also can work reliably.Because these the three groups of moving elements of piston type air distributing device, gas compressor and gas-turbine in the air turbine of the present invention can both be stablized permanent running, this is very important to the power plant as power plant.
Description of drawings is described in further detail air turbine of the present invention below in conjunction with accompanying drawing.
Fig. 1 is the sectional drawing of first kind of mode of execution of cooling isobaric heat sucking type air turbine among the present invention.
Fig. 2 is the local amplification profile of tie-beam and set roller row in the air turbine shown in Figure 1.
Fig. 3 is the row's of roller shown in Fig. 2 a plan view
Fig. 4 is the side cutaway view of preheater in the air turbine shown in Figure 1.
Fig. 5 is along the sectional view of A-A line among Fig. 4
Fig. 6 is the structural configuration sketch of cooling isobaric heat sucking type air turbine second mode of execution among the present invention.
Fig. 7 is the Btu utilization and the loss flow graph of cooling isobaric heat sucking type air turbine among the present invention.
Fig. 8 is the sectional drawing of cooling isobaric heat sucking type air turbine the 3rd mode of execution among the present invention.
Embodiment Fig. 1 to Fig. 5 shows first mode of execution of cooling isobaric heat sucking type air turbine among the present invention.This air turbine comprises interstage cooler 14, heater 36, boiler 41, gas compressor 8 and the gas-turbine 28 that links to each other through main shaft 26, and heater 36 is located in the boiler 41 that uses solid fuel.When adopting other external heat source (as nuclear reactor), heater is located in the high-temperature exhaust air or Drainage pipe of this external heat source.For carrying out the endothermic process of isopiestic state, between interstage cooler 14 and heater 36, be provided with air distributing device 48, air distributing device is made of the rotary cylinder-block 76 of shell 49 and Qi Nei, rotary cylinder-block is contained on the central shaft 62 of fixedlying connected with shell 49, is respectively equipped with on it around the little secondary cylinder 82 of the band cold aeration mouth 83 of central shaft annular array and first mate's cylinder 92 of the hot ventilating hole 93 of opposite side band.Corresponding big or small gas distribution pistons 95,85 link to each other with turnover swash plate 66 transmissions on the central shaft 62 by connecting rod in first mate's cylinder 92 and the little secondary cylinder 82.Be provided with gear 77 on rotary cylinder-block 76, central gear 27 driven gears 77 on the main shaft 26 rotate rotary cylinder-block.When rotary cylinder-block 76 rotates, the cold aeration mouth 83 on the little secondary cylinder 82 can be respectively with the little valve disc 50 of shell 49 sides on set inflation inlet 51 and ventilation outlet 53 link up mutually; Hot ventilating hole 93 on first mate's cylinder 91 can be respectively with the big valve disc 56 of shell opposite side on set ventilation import 58 and air outlet 60 link up mutually.
Each parts general arrangement of cooling isobaric heat sucking type air turbine as shown in Figure 1 among the present invention, the inflation inlet 51 of the outlet passageway 11 of gas compressor 8 on the little valve disc 50 of interstage cooler 14 and air distributing device is connected, the ventilation of little valve disc outlet 53 by the road 55, heater 36 and heat insulating tube 38 be connected with ventilation import 58 on the big valve disc 56, and the suction port of gas-turbine 28 is led in the air outlet 60 of valve disc through pressure heat insulating tube 61 greatly.Because what adopt in the present embodiment is that boiler is as external heat source, for fully recycling the heat of compression that gas compressor 8 is produced, the interstage cooler 14 of gas compressor back has been located in the cooling air jacket 18 with the reflux type heat exchange, and the pipeline 23 of the heat radiation air outlet slit 21 of coolant jacket through being provided with blower 24 leads to the corresponding intake grill 42 of boiler 41.After the resulting higher temperature heat radiation of cold heat exchange air was introduced into boiler participation burning in the adverse current, the heat loss that cooling is produced in the middle of can making was recycled by major part, and gas compressor reduces the compression work that is consumed because of cooling off in the middle of carrying out significantly.In first mode of execution shown in Figure 1, gas compressor 8 has been located at the back of gas-turbine 28, and the suction port positioned opposite of the relief opening of gas-turbine and gas compressor 8 is communicated with by being communicated with letter road 35 between two gas ports, thereby has constituted a kind of enclosed air circulation system.For reclaiming the exhaust gas heat of gas-turbine 28, improve the air inlet state of gas compressor 8, in being communicated with letter road 35, also be provided with air preheater 104, the pipeline 108 of the exhaust port 107 of preheater through being provided with blower 109 leads to the corresponding intake grill 43 of boiler 41.Obviously, be to obtain the preheated air of higher temperature, the blast air of air preheater 104 and gas-turbine 28 is with the reflux type heat exchange, and, set blower 109 also should have speed-regulating function, so as to reduce at power, delivery temperature corresponding cooling air quantity of turning down when also reducing.
In of the present invention in the cooling isobaric heat sucking type air turbine running, the middle cooling procedure of being undertaken by interstage cooler 14 and two cyclic processes that separated by air distributing device 48 and mutually promote by the isobaric heat absorption process that heater 36 is carried out, through in compressed air temperature after cold low more, the compression work that gas compressor 8 is consumed is also few more, also helps more allowing heater 36 absorb more heat from boiler simultaneously.For allowing smooth the passing through of gas energy that passes in and out big or small secondary cylinder, in the air-breathing and exhaust stroke of little secondary cylinder 82, the cold aeration mouth 83 of little secondary cylinder can be respectively with the little valve disc 50 of shell on inflation inlet 51 and ventilation outlet 52 link up angles (the cold aeration mouth can not be linked up inflation inlet and ventilation outlet simultaneously) near 180 °.In first mate's cylinder 92 intake processes, it is 180 ° that the hot ventilating hole 93 of first mate's cylinder is linked up angle with the ventilation import 58 on the big valve disc 56.And in first mate's cylinder 92 exhaust processes, promptly can connect with hot ventilating hole 93 in the air outlet 60 big gas distribution piston 95 allows big valve disc when lower dead center moves up on, also can suitably reduce the shared angle of air outlet 60, allow work done gases in 95 pairs of first mate's cylinders of big gas distribution piston 92 carry out to a certain degree compression earlier, the work done gas that allows pressure improve is again gone out from the air outlet 60 of opening through hot ventilating hole, promotes turbine 28 external works done.Certainly, can not allow too many that the shared angles in air outlet 60 reduce, with the difficulty avoiding sealing greatly with increase the turnover mechanical load that swash plate was born.
Because cooling isobaric heat sucking type air turbine can be made into very big power usually in of the present invention when being used for power plant,, except that the size that increases air distributing device, mainly be by increasing the quantity of air distributing device for adapting to the big Flow characteristics of gas-turbine 28.Set air distributing device 48 can be around main shaft 26 symmetries (two time) or ring-like layout, and the air outlet 60 on it is relative with the suction port of gas-turbine 28 and be communicated with through pressure heat insulating tube 61.Still do not reach required displacement as this layout, can also establish one group of identical air distributing device (drawing among the figure) in the outside of the air distributing device 48 of above-mentioned symmetry or ring-like layout again, and the angle that allows this assembly device of air and inboard air distributing device stagger certain installs, so as to allow its go up each corresponding air outlet 60 respectively the lengthening pressure heat insulating tube through passing space, inboard air distributing device interval lead to the suction port of gas-turbine 28.Simultaneously, for driving the air distributing device in the outside, the main shaft 26 of lengthening also drives the gear 77 on the rotary cylinder-block 76 in each air distributing device of the outside by the central gear in the outside.
In air distributing device 48, for simplifying the structure of driving mechanism, the big gas distribution piston 95 of each of rotary cylinder-block 76 is connected as a single entity through tie-beam 86 and corresponding little gas distribution piston 85 respectively, turnover swash plate 66 links to each other with big gas distribution piston by connecting rod 96, and the inboard of tie-beam 86 has the recessed portion 87 of avoiding turnover swash plate 66.For allowing rotary cylinder-block adapt to higher rotating speed, and reduce big or small gas distribution piston and tie-beam because of surface friction drag that very big centrifugal force produced, as shown in Figure 2, on the outer side surface of tie-beam, be provided with slide rail 88, be provided with a rail 80 and connect on the inner side surface opposite position of shell 78, between the slide rail of tie-beam and a rail that is connected shell, set up roller and arranged 98 at rotary cylinder-block.Set roller row 98 constitutes (referring to Fig. 3) by retainer 100 and roller 99, for allowing roller row 98 in moving back and forth, can remain on the mobile position of regulation with tie-beam 86, on retainer 100, be provided with several double installation shaft 102 (carrying out single layout in the middle of also installation shaft can being located at) two layouts, identical intermediate gear 101 is housed on the installation shaft, respective rack 81,89 set on these gears and seat rail and the slide rail is meshed.Set roller row 98 is just for overcoming bigger centrifugal action, also can allow the bi-side of tie-beam 86 form slide rail, and match with corresponding rail level on being connected shell, so just can allow big or small gas distribution piston only contact with cylinder inner wall by piston ring, and needn't be lubricated by between, to keep the cleaning of inner loop air.Heavier because of big gas distribution piston 95 side quality, to increase certain counterweight in little gas distribution piston side in the reality.
For the air preheater 104 in the letter road 35 of being communicated with that is located between gas-turbine 28 and the gas compressor 8, as shown in Figure 4 and Figure 5, mainly taked to help reducing the mode of structure of gas-flow resistance, this air preheater constitutes these heat absorption flat tubes by the heat absorption flat tube 112 of some quantity and has suitable length and in-line arrangement air-flow in the connection letter road 35 that is located at annular, each flat tube that absorbs heat is radial with its cross section in annular is communicated with the letter road arranges, some the passive endothermic plates of being arranged by the in-line arrangement airflow direction between each adjacent heat absorption flat tube 112 113 link to each other.The continuous whole preheater structure that constituted an annular of the above-mentioned flat tube that respectively absorbs heat by endothermic plate, the turning point front end and the afterbody of each flat tube that absorbs heat are streamline shape.
Fig. 6 is the second mode of execution sketch of cooling isobaric heat sucking type air turbine among the present invention, different with first mode of execution, in second mode of execution, the exhaust passage 34 of gas-turbine 28 has been drawn towards the corresponding intake grill 43 of boiler 41, allow air participates in burning by entering boiler after the work done that has certain waste heat that gas-turbine discharges, airborne heat is fully absorbed, to reduce the fuel consumption in the boiler.In the air turbine that output power often changes, on exhaust passage 34, also be provided with venting valve (not drawing among the figure), so that Open valve is suitably exitted when power reduces, cooperate boiler 41 to adjust the combustion heating amount of fuel 47.What this air turbine among Fig. 6 adopted is the open cycle arrangement.
Describe below in conjunction with the working procedure of Fig. 6 second mode of execution cooling isobaric heat sucking type air turbine among the present invention, this air turbine comprises isothermal compression, isobaric heat absorption and three processes of expansion working, and isothermal compression wherein and isobaric heat absorption are the cyclic processes that can mutually promote that is spaced and carries out.
(1) isothermal compression process gas compressor 8 is compressing from import 10 inhaled airs, and the low temperature pressurized air (being lower than 60 ℃) that is produced by interstage cooler 14 backs enters the little secondary cylinder 82 that is in suction condition along outlet passageway 11 along arrow 17 directions through inflation inlet 51.Little gas distribution piston 85 row in little secondary cylinder 82 when lower dead center has been full of the compressed-air actuated little secondary cylinder of low temperature and has also turned over inflation inlet 51, the end of isothermal compression process.
Isothermal compression allows the heat of compression that gas compressor 8 produced in compression process by interstage cooler 14 guiding cooling air jackets 18, and the compressed air temperature and the pressure of compression terminal state are reduced significantly.The reduction of compressed air temperature is for the isobaric heat absorption process of being carried out provides maximum temperature difference; And the reduction of compressed air pressure has then reduced the compression work that gas compressor consumed significantly, has improved the compressive state of gas compressor.
When utilizing boiler 41 as the external heat source of heater 36, carrying out the heat of compression that isothermal compression produced can not dissipate in vain yet, but utilize the cooling air jacket 18 of countercurrent flow fully to reclaim, and then allow the heat radiation air of temperature rising introduce boilers 41 participation burnings, thereby the consumption of corresponding reduction fuel by blower 24.
(2) this process of isobaric heat absorption process is to utilize the exhaust of little secondary cylinder 82 and the breathing process of first mate's cylinder 92 to realize, rotate when beginning to carry out exhaust with rotary cylinder-block when being full of the compressed-air actuated little secondary cylinder 82 of low temperature, cold aeration mouth 83 on it is also linked up with ventilation outlet 53, the little gas distribution piston 85 that moves up is just arranged into heater 36 to the low temperature pressurized air in the little secondary cylinder along arrow 39 directions, is heated by the combustion gas in the boiler 41.Meanwhile, it is air-breathing that big gas distribution piston 95 in the opposite side first mate cylinder 92 that heater via is linked up moves forward into row to lower dead center, allows be filled into first mate cylinder 92 through heat insulating tube 38 arrows 40 directions from ventilation import 58 by the high temperature work done air (600 ℃) after heater 36 heating.Because of the volume of first mate's cylinder greater than little secondary cylinder, the low temperature pressurized air volume that is heated by heater just can be expanded in first mate's cylinder accordingly, and the gas pressure in the heating circulation system is not risen, and allows endothermic process carry out at isopiestic state.The capable big gas distribution piston in top dead center, first mate's cylinder of little gas distribution piston in little secondary cylinder is capable to lower dead center and after being full of high temperature work done air, and the isobaric heat absorption process finishes.
Because of isobaric heat absorption, the low temperature compressed air temperature that just enters in the heater 36 is not raise, still absorb corresponding heat the combustion gas that can reduce from the temperature that flows through the heater periphery soon, allow the heat in the combustion gas that boiler produced to be exhausted substantially, thereby improved the utilization ratio of fuel heat, also increased the heat absorption potentiality of heater.
When carrying out the isobaric heat absorption process, at the same time by in the big or small secondary cylinder of UNICOM, because of the difference of big or small gas distribution piston area, big gas distribution piston 95 can be pushed corresponding work done, can produce the driving force that driven rotary cylinder body 76 is rotated self at least.
(3) after expansion working process first mate's cylinder 92 of finishing, be full of high temperature work done air in the isobaric heat absorption process forwards the position of linking up mutually with air outlet 60 to, big gas distribution piston 95 in it is just arranged high temperature work done air to gas-turbine 28 along arrow 94 directions, the promotion gas-turbine rotates, and drives gas compressor 8 and rotary cylinder-block 76 runnings and externally work done.The air that still has uniform temperature of discharging from gas-turbine 28 then 34 enters boiler 41 along arrow 33 directions and participates in burning through the exhaust passage.
In isothermal compression, isobaric heat absorption and the expansion working process that above-mentioned air turbine carried out, the favorable factor that can improve the thermal efficiency mainly comprises two aspects, at first be that isobaric heat absorption can exhaust the heat that boiler produces substantially, next is an isothermal compression, it not only allows the exhaust gas heat of the heat that distributed in the minimum but also compression process of compression work that gas compressor consumed and gas-turbine can both be introduced into boiler and reclaims, and allows heat that air turbine of the present invention lost seldom.
The Btu utilization of cooling isobaric heat sucking type air turbine in cyclic process and loss flow graph are as shown in Figure 7 among the present invention, after 100% fuel heat has been lost 10% by the boiler heat extraction, remaining 90% is absorbed by heater, and the heat extraction radiation loss that the heat that heater absorbs is produced during cooling in the middle of gas-turbine work done exhaust and gas compressor is 25%.But owing to adopt boiler, in 25% radiation loss, can there be 15% heat fully to be reclaimed, makes the fuel heat utilization ratio of gas-turbine bring up to 80% from 65% in the mode of returning boiler and participating in burning as external heat source.In above analysis, though be preliminary EFFICIENCY PREDICTION to air turbine of the present invention, as long as but adjust balance between boiler heating value and the heater caloric receptivity, allow the combustion gas of adverse current heating discharge boiler with very low temperature (80 ℃～100 ℃), simultaneously, heat in centre cooling and the gas-turbine exhaust is also fully reclaimed and guide into boiler, just can allow this air turbine overall efficiency of the present invention reach high state.Because heat loss is very little, reaching 70% effective efficiency in the reality should be easily, can be to large scale development thereby air turbine of the present invention is become, and can substitute the effectively power device of steam power system in the common power plant comprehensively.
What Fig. 8 described is the third mode of execution of cooling isobaric heat sucking type air turbine among the present invention, the air turbine of this mode of execution also is to adopt open cycle, atmosphere is led in the exhaust passage 34 of the relief opening of gas-turbine 28 through being provided with air preheater 104, the pipeline 108 of the exhaust port of air preheater through being provided with blower 109 leads to the corresponding intake grill 43 of boiler 41, to reclaim the heat in gas-turbine 28 exhausts.
In the present embodiment, also be provided with the bypass line 70 of band firing chamber 68 in the periphery of the pressure heat insulating tube 61 that is connected with air distributing device air outlet 60, between the import of bypass line and pressure heat insulating tube 61, be provided with oscillatory valve 72, like this, strengthen output power in short-term at needs, when allowing the firing chamber carry out oil jetting combustion, the oscillatory valve 72 that matches just can be from cutting out the state of bypass line 70, corresponding to swing (shown in dotted line oscillatory valve position among the figure) in the pressure heat insulating tube 61, allow firing chamber 68 obtain the required thermal air current that burns.This structure scheme is a kind ofly to comprise external combustion and internal combustion and based on the compound recycle mode of external combustion.
Owing to adopt the air turbine variable power scope of combined cycle bigger, in order to allow the air preheater 104 of gas-turbine 28 back can fully effectively reclaim heat contained in the exhaust, blower 109 is controlled by arrangements for speed regulation 115, temperature information according to temperature transducer set on the exhaust passage 34 116, rotating speed that can corresponding increase blower when high-power, allow the interior air-flow of air preheater flow fast, so that can reclaim more heats the high-temperature exhaust air in the exhaust passage.
As simplification improvement design to the 3rd mode of execution, also can with pressure heat insulating tube 61 that air distributing device air outlet 60 is connected on tail pipe burner (drawing among the figure) directly is set, also telescopic fuel injector to be set simultaneously, so that allow fuel injector put in the tail pipe burner oil jetting combustion when needed, to increase the power output of air turbine in short-term.
More than three different mode of executions of cooling isobaric heat sucking type air turbine among the present invention have been carried out sufficient explanation, the heat loss that produced seldom because this air turbine of the present invention is in operation, to become power plant's generation power device of fuel saving, create necessary condition for reducing discharge of carbon dioxide greenhouse gas significantly.Because of the used heat that produced seldom, this novel power device need not established cooling tower used in the common steam power plant, can a large amount of heat extractions in atmosphere or seawater yet.And make working medium with air, and also can break away from dependence to water, make the addressing institute of power plant restricted minimum.Certainly, this air turbine of the present invention not only is suitable for the power plant as power plant, also is fully feasible as power plant in big-and-middle-sized boats and ships and ground power source.
Claims (10)
1, a kind of middle cooling isobaric heat sucking type air turbine, it comprises interstage cooler (14), heater (36), boiler (41), gas compressor (8) and the gas-turbine (28) that links to each other through main shaft (26), heater (36) is located in the boiler (41), perhaps is located in the high-temperature exhaust air or Drainage pipe of other thermal source.It is characterized in that: it also comprises the air distributing device (48) that several are made of shell (49) and the rotary cylinder-block (76) in it, rotary cylinder-block (76) is contained on the central shaft (62) of fixedlying connected with shell (49), be respectively equipped with on it around the little secondary cylinder (82) of the band cold aeration mouth (85) of central shaft annular array and first mate's cylinder (92) of the hot ventilating hole of opposite side band (93), corresponding big or small gas distribution piston (95 in first mate's cylinder (92) and the little secondary cylinder (82), 85) link to each other with turnover swash plate (66) transmission on the central shaft (62) by connecting rod, rotary cylinder-block (76) is driven by the central gear (27) on the main shaft (26) through the gear on it (77); When rotary cylinder-block (76) rotates, cold aeration mouth (83) on the little secondary cylinder (82) can be gone up set inflation inlet (51) and take a breath (53) with the little valve disc (50) of shell (49) side respectively and link up mutually, and the hot ventilating hole (93) on first mate's cylinder (92) can be gone up set ventilation import (58) and air outlet (60) with the big valve disc of shell (49) opposite side (56) respectively and link up mutually; The inflation inlet (51) of the outlet passageway (11) of described gas compressor (8) on the little valve disc (50) of interstage cooler (14) and air distributing device is connected, the ventilation of little valve disc outlet (53) (55), heater (36) and heat insulating tube (38) by the road is connected with ventilation import (58) on the valve disc greatly, greatly the air outlet (60) of the valve disc suction port that leads to gas-turbine (28) through pressure heat insulating tube (61); When adopting boiler to make external heat source, interstage cooler (14) is located in the cooling air jacket (18) with the reflux type heat exchange, and the pipeline (23) of the heat radiation air outlet slit (21) of coolant jacket through being provided with blower (24) leads to the corresponding intake grill of boiler (41).
2, air turbine according to claim 1, it is characterized in that: in described air distributing device, each big gas distribution piston (95) in the rotary cylinder-block (76) is connected as a single entity through tie-beam (86) and corresponding little gas distribution piston (85) respectively, the inboard of tie-beam has the recessed portion (87) of avoiding the turnover swash plate, on the outer side surface of tie-beam, be provided with slide rail (88), on the inner side surface opposite position of rotary cylinder-block connection shell (78), be provided with a rail (80), the roller row (98) who is constituted with retainer (100) and roller (99) is housed between present rail and the slide rail; Be provided with the single installation shaft (102) of several double or intermediate arrangement of arranging in both sides on retainer (100), identical intermediate gear (101) is housed on the axle, respective rack set on these gears and a rail and the slide rail is meshed.
3, air turbine according to claim 2 is characterized in that: described air distributing device (48) is around main shaft (26) symmetry or ring-like layout, and the suction port of the air outlet on it (60) and gas-turbine (28) is relative and be communicated with through pressure heat insulating tube (61).
4, air turbine according to claim 3, it is characterized in that: one group of identical air distributing device is established in the outside at the symmetry or the air distributing device (48) of ring-like layout again, the angle that the air distributing device of this assembly device of air and inboard staggers certain is installed, allow each corresponding air outlet (60) on it respectively through passing the inboard air distributing device lengthening pressure heat insulating tube in the space suction port that leads to gas-turbine (28) at interval, the main shaft of lengthening (26) drives the gear (77) on the rotary cylinder-block (76) in the air distributing device by the central gear (27) in the outside.
5, according to claim 3 or 4 described air turbines, it is characterized in that: gas compressor (8) is located at the rear portion of gas-turbine (28), the import positioned opposite of the relief opening of gas-turbine and gas compressor, be communicated with by being communicated with letter road (35) between two gas ports, be provided with air preheater (104) in being communicated with letter road (35), the pipeline (108) of the exhaust port of preheater through being provided with blower (109) leads to the corresponding intake grill of boiler (41).
6, air turbine according to claim 5, it is characterized in that: set air preheater (104) is made of the heat absorption flat tube (112) of some quantity, these heat absorption flat tubes have suitable long length and in-line arrangement air-flow in the connection letter road (35) that is located at annular, each flat tube that absorbs heat is radial with its cross section and arranges in annular is communicated with the letter road, some the endothermic plates of being arranged by downstream direction between each adjacent heat absorption flat tube (112) (113) link to each other, the continuous whole preheater structure that constituted an annular of each flat tube that absorbs heat by endothermic plate, the turning point front end and the afterbody of each flat tube that absorbs heat are streamline shape.
7, according to claim 3 or 4 described air turbines, it is characterized in that: the corresponding intake grill of boiler (41) is led in the exhaust passage (34) of gas-turbine (28), the venting valve of opening when being provided with low-power on the exhaust passage.
8, according to claim 3 or 4 described air turbines, it is characterized in that: the external world is led in the exhaust passage (34) of the relief opening of gas-turbine (28) through being provided with air preheater (104), and the pipeline (108) of the exhaust port of air preheater through being provided with blower (109) leads to the corresponding intake grill of boiler (41).
9, air turbine according to claim 8, it is characterized in that: the bypass line (70) that is provided with band firing chamber (68) in the periphery of the pressure heat insulating tube (61) that is connected with air distributing device air outlet (60), between the import of bypass line and pressure heat insulating tube (61), be provided with oscillatory valve (72), when burn in the firing chamber, oscillatory valve (72) swings in the pressure heat insulating tube accordingly from cutting out the bypass line position.
10, air turbine according to claim 8 is characterized in that: with pressure heat insulating tube (61) that air distributing device air outlet (60) are connected on be provided with tail pipe burner, set telescopic fuel injector puts in tail pipe burner when burner oil.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007100974047A CN101050714A (en) | 2007-05-09 | 2007-05-09 | Medium cooling isobaric heat sucking type air turbine |
| PCT/CN2008/000920 WO2008138221A1 (en) | 2007-05-09 | 2008-05-09 | Intercooling equipressure heat-of-absorption type air turbine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2007100974047A CN101050714A (en) | 2007-05-09 | 2007-05-09 | Medium cooling isobaric heat sucking type air turbine |
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| CN101050714A true CN101050714A (en) | 2007-10-10 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNA2007100974047A Pending CN101050714A (en) | 2007-05-09 | 2007-05-09 | Medium cooling isobaric heat sucking type air turbine |
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| Country | Link |
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| CN (1) | CN101050714A (en) |
| WO (1) | WO2008138221A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008138221A1 (en) * | 2007-05-09 | 2008-11-20 | Peizhou Han | Intercooling equipressure heat-of-absorption type air turbine |
| CN114506828A (en) * | 2022-01-19 | 2022-05-17 | 福建华清电子材料科技有限公司 | Low-cost aluminum nitride powder preparation process |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB569441A (en) * | 1942-09-10 | 1945-05-24 | Oerlikon Maschf | Improvements in or relating to combustion plant |
| GB604392A (en) * | 1944-11-14 | 1948-07-02 | Oerlikon Maschf | Improvements in or relating to a power plant |
| GB711271A (en) * | 1950-08-18 | 1954-06-30 | W H Allen Sons & Company Ltd | Improvements in or relating to waste heat recovery installations |
| JP2000045711A (en) * | 1999-07-05 | 2000-02-15 | Babcock Hitachi Kk | Pressurized fluidized bed boiler compound power generating equipment |
| JP4395254B2 (en) * | 2000-11-13 | 2010-01-06 | 三菱重工業株式会社 | Combined cycle gas turbine |
| CN101050714A (en) * | 2007-05-09 | 2007-10-10 | 韩培洲 | Medium cooling isobaric heat sucking type air turbine |
| CN101050727A (en) * | 2007-05-09 | 2007-10-10 | 韩培洲 | Medium cooling isobaric backheating gas turbine |
| CN101078358A (en) * | 2007-06-28 | 2007-11-28 | 韩培洲 | Intercooled isotonic decalescence air turbine with denitration flow path |
| CN101144395A (en) * | 2007-10-15 | 2008-03-19 | 韩培洲 | Nuclear energy intercooled equal-pressure heat-absorption air turbine |
-
2007
- 2007-05-09 CN CNA2007100974047A patent/CN101050714A/en active Pending
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2008
- 2008-05-09 WO PCT/CN2008/000920 patent/WO2008138221A1/en active Application Filing
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008138221A1 (en) * | 2007-05-09 | 2008-11-20 | Peizhou Han | Intercooling equipressure heat-of-absorption type air turbine |
| CN114506828A (en) * | 2022-01-19 | 2022-05-17 | 福建华清电子材料科技有限公司 | Low-cost aluminum nitride powder preparation process |
| CN114506828B (en) * | 2022-01-19 | 2024-02-27 | 福建华清电子材料科技有限公司 | Low-cost aluminum nitride powder preparation process |
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| WO2008138221A1 (en) | 2008-11-20 |
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