CN201884127U

CN201884127U - Vortex gas-steam turbine

Info

Publication number: CN201884127U
Application number: CN2010206668165U
Authority: CN
Inventors: 杜臣
Original assignee: Individual
Current assignee: Individual
Priority date: 2010-12-14
Filing date: 2010-12-14
Publication date: 2011-06-29
Anticipated expiration: 2020-12-14

Abstract

The utility model relates to a vortex gas-steam turbine, which belongs to the field of heat engines and solves the problems that efficiency increase of a gas turbine is limited and boiler heat exchange efficiency and rate of a steam turbine are low because of reduction of effective enthalpy of a constant-pressure combustion heat-absorptive gas turbine. Serial multistage vortex superchargers are respectively arranged between a gas compressor and a combustion chamber of the vortex gas-steam turbine, between the combustion chamber and a high-pressure turbine, and among the high-pressure turbine, a medium-pressure turbine and a low-pressure turbine, a wedged regulating device is connected in series to each of the vortex superchargers and gas inlet and outlet passages of the combustion chamber, a high-pressure turbine shaft is in transmission connection with a gas compressor shaft through an overrun clutch, and a shaft output power source is connected to a medium-pressure turbine shaft and a low-pressure turbine shaft via differential couplings in a differential manner. The vortex gas-steam turbine realizes combustion heat absorption and flash mixed heat exchange in variable states, and realizes conversion of medium internal energy to kinetic energy and conversion of kinetic energy to potential energy, so that medium pressure is higher than average heat absorption temperature corresponding pressure ratio, deep enthalpy reduction is realized, and the vortex gas-steam turbine is applicable to aviation, vehicles and vessels, oil-gas transmission pipeline boosting, power supply, mobile power plants and the like.

Description

Vortex combustion and steam turbine

Technical field

The utility model relates to a kind of combustion and steam turbine, and being specifically related to a kind of is working medium with the gas-air steam mixture, and vortex combustion and steam turbine is controlled in the changeable burning heat absorption of permanent Continuous Flow, mixing heat exchange of flash evaporation, vortex supercharging totally, belongs to hot machine technology field.

Background technique

Gas turbine than height ratio merit, good mobility, is widely used in occasions such as Aero-Space, naval vessel, oil and gas pipeline supercharging, mobile power station, peak load regulation network generating with it.The gas turbine of using all adopts constant-pressure type burning heat absorption at present, and working medium is a large amount of high-temperature low-pressure gas-air mixtures, and effective enthalpy reduces, and exhaust heat leaving loss is big, has limited the raising of gas turbine proficiency; Higher average endothermic temperature, the use of a large amount of high temperature resistant precious metals has determined that the working life of unit is short, the operation poor reliability makes it can not get extensive use in the comprehensive economy occasion of having relatively high expectations.

Steam turbine efficient improves the application that depends on high parameter steam, and along with the raising of vapor pressure, the corresponding temperature that improves saturated vapour certainly will be dwindled boiler heat-transfer face temperature difference, will increase considerably a pot plate thickness simultaneously; The increase and the heat transfer surface temperature difference of pot plate thickness are dwindled, and effect all is to reduce the coefficient of overall heat transmission, thereby reduces efficiency of boiler.Because this heat transfer surface and the heat transfer surface both sides heat-conduction medium temperature difference exist, this heat exchange mode and a large amount of low-grade toxic emission are restricting the raising of steam turbine efficient.

Support that hot mechanism opinion is thermomechanics three laws and Carnot's cycle theory.Carnot's cycle can be expressed as: " hot machine must be at least functioning between two thermals source, and from the high temperature heat source draw heat, and wherein a part is passed to low-temperature heat source, could obtain mechanical work like this " " promptly works in same high temperature heat source T ₁With low-temperature heat source T ₂Between the efficient of all reversible Carnot Engine:

(select from nineteen eighty-three the Wu of Shanghai science tech publishing house must, happy " calorifics " the 223rd page and the 226th page of compiling of this song); The hot machine of using all is low-temperature heat source with the environment at present; People can't change ambient temperature, according to the Kano theory, so improve average endothermic temperature as far as possible, but efficiency of heat engine improves and theoretical value greatly differs from each other, it is found that average relatively endothermic temperature has a corresponding pressure ratio, the corresponding pressure ratio of average endothermic temperature is restricting the effectively height of enthalpy drop, so improve the pressure of medium again as far as possible, but when pressure ratio improves, average endothermic temperature also can correspondingly improve, always do not reach the corresponding pressure ratio of average endothermic temperature, effectively the enthalpy drop and the thermal efficiency improve then very limited; People pace up and down in this vicious circle since nearly half a century, and efficiency of heat engine does not have big breakthrough.

The model utility content

The utility model purpose provides a kind of vortex combustion and steam turbine, adopt the gas turbine effective enthalpy of constant-pressure type burning heat absorption to reduce the heat transmission equipment coefficient of overall heat transmission and the inefficient low problems of speed such as the raising of restriction gas turbine proficiency and steam turbine boiler to solve.

For solving the problems of the technologies described above the technological scheme of taking be: vortex combustion and steam turbine of the present utility model comprises Starter, Starter clutch, gas compressor, firing chamber, ratchet type overrunning clutch, cover shaft type differential coupling, high pressure turbine, intermediate pressure turbine and low pressure turbine; Described vortex combustion and steam turbine also comprises turbocharger, vortex venting gas appliance, solid-liquid body segregating unit, wedge-like body regulating controller; Described turbocharger is formed by being arranged on the 4th group of multistage turbocharger of connecting that is provided with between the 3rd group of multistage turbocharger of connecting being provided with between second group of multistage turbocharger of connecting being provided with between first group of multistage turbocharger of connecting between gas compressor and firing chamber and firing chamber and high pressure turbine, high pressure turbine and intermediate pressure turbine, intermediate pressure turbine and low pressure turbine; Be respectively arranged with a wedge-like body regulating controller on the inlet and outlet passage of described turbocharger and firing chamber, first order turbocharger and vortex venting gas appliance in the multistage turbocharger of every group of series connection are provided with a solid-liquid body segregating unit; Solid-liquid body segregating unit is respectively the first solid-liquid body segregating unit, the second solid-liquid body segregating unit and the 3rd solid-liquid body segregating unit, and the first solid-liquid body segregating unit, the second solid-liquid body segregating unit are identical with the 3rd solid-liquid body segregating unit structure;

The Starter output shaft of Starter is in transmission connection by an end of the compressorshaft of Starter clutch and gas compressor, and an end of the high pressure turbine axle of high pressure turbine is in transmission connection by the other end of the compressorshaft of ratchet type overrunning clutch and gas compressor; The cover shaft type low pressure turbine axle of the intermediate pressure turbine axle of intermediate pressure turbine and low pressure turbine is affixed with two taper driving gears of cover shaft type differential coupling respectively, and power is by the stub output of cover shaft type differential coupling; The connection of joining of the annular waste air duct of gas compressor and the annular inlet passageway of first group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of first group of series connection is joined with the annular inlet passageway of firing chamber and is communicated with, the connection of joining of the annular waste air duct of firing chamber and the annular inlet passageway of second group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of second group of series connection is joined with the annular inlet passageway of high pressure turbine and is communicated with, the connection of joining of the annular waste air duct of high pressure turbine and the annular inlet passageway of the 3rd group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of the 3rd group of series connection is joined with the annular inlet passageway of intermediate pressure turbine and is communicated with, the connection of joining of the annular waste air duct of intermediate pressure turbine and the annular inlet passageway of the 4th group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of the 4th group of series connection is joined with the annular inlet passageway of low pressure turbine and is communicated with, the annular waste air duct of low pressure turbine is joined with the annular inlet passageway of vortex venting gas appliance and is communicated with, and the relief opening of vortex venting gas appliance is communicated with atmosphere.

Burning heat absorption under the mixed combustion section air of firing chamber and the changeable state of fuel in permanent continuous vortex flow; Under same changeable state, high-temperature fuel gas air mixture and an amount of high-pressure atomization clean water fine drop surface directly contact the flash vaporization mixed heat transfer in firing chamber mixing exhaust section; In described turbocharger, eddy combustion chamber and vortex venting gas appliance, medium is dynamically compressed in permanent continuous vortex flow, can change the kinetic energy of medium in the part of medium earlier into, and kinetic energy changes the potential energy of medium again into; Cover shaft type differential coupling by the planetary differential rotation of cover shaft type differential coupling each is inserted the axle revolution and enthalpy drop is carried out the self adaption dynamic adjustments; Two input shafts of described cover shaft type differential coupling when the unpowered input of a side, can be prevented reversing automatically; Described vortex combustion and steam turbine all devices is by a computer regulating center and a plurality of execution and the unified control of servomechanism.

The utility model is to solve the problems of the technologies described above the technological means of taking to be: the utility model is at first realized a kind of changeable burning heat absorption of permanent Continuous Flow in the firing chamber.In changeable burning endothermic process, temperature, pressure, the specific volume of medium (air or gas-air water vapor mixture) all change, and the pressure of realization is comparatively near the corresponding pressure ratio of average endothermic temperature.Realize this process, can adopt stifled way on the exhaust combustion chamber passage, but can not block fully, must permanent continuous-flow, resemble the barrage in water power plant; The Rafael nozzle threshold state just can produce this effect, when Rafael nozzle throat air-flow reaches velocity of sound, Rafael nozzle promptly is in threshold state, in the critical pressure ratio scope, increase jet pipe upstream pressure chamber pressure and reduce jet pipe downstream back pressure chamber pressure, Rafael nozzle throat airspeed will remain unchanged, thereby the volume flow of Rafael nozzle remains unchanged, increase or reduce the mass flow rate of pressure chamber's pressure corresponding increase of meeting or minimizing Rafael nozzle, reduce or increase back pressure chamber pressure, the back pressure chamber pressure disturbance can not upload to the pressure chamber, because pressure disturbance also is a kind of pressure wave, pressure wave is propagated with velocity of sound, the north propagation in the not meeting of pressure disturbance of velocity of sound and supersonic airstream middle and lower reaches, thus the volume of Rafael nozzle and mass flow rate remain unchanged.In the critical section scope, increase or reduce the Rafael nozzle throat section, can corresponding increase or reduce the volume flow of Rafael nozzle; Use Rafael nozzle critical effect (throat's flow velocity is constant under the threshold state, volume flow keeps and the check effect is uploaded in the downstream pressure disturbance), the adjustable Rafael nozzle in throat section is set on the exhaust combustion chamber passage, can under the Rafael nozzle threshold state, effectively regulate and control chamber pressure in real time, the volume of firing chamber and mass flow rate realize the permanent continuous-flow of medium simultaneously.The utility model is released adjustable position variant wedge-like body regulating controller and the deformation formula wedge-like body regulating controller in throat section, cooperates particular airflow channel design shape line, can realize the Rafael nozzle critical effect under threshold state.Chamber pressure raises, adverse current upstream, and the medium that is lower than chamber pressure can not enter the firing chamber, and this is this respect research in the past and the basic reason of exploring failure; In fact there is several different methods to address this problem; Method one is a pumping over, uses moving blades fluid pumping over and check effect, and axial flow and centrifugal-flow compressor are used this effect work; Big pressure reduction check pumping over requires the leaf grating angle of attack minimum, rigidity is very big, bigger stable work area is arranged, the lamination interlayer small structure that the tubular revolving combustor that the utility model is released and the flame tube wall of ring rotation firing chamber and end plate thereof, fagging adopt, can satisfy this requirement, revolving combustor is realized changeable burning heat absorption under moving blades fluid pumping over and check effect and the effect of Rafael nozzle critical effect, mix heat exchange of flash evaporation; Method two is to induce, and when leaf grating or class leaf grating body axis and fluid vectors direction angle are spent less than 90, according to relativity principle, can produce above-mentioned effect, induces medium to enter the high voltage control district by low pressure area, and described angle is more little, and liquid speed is high more, and effect is remarkable more; Method three, another induces mode, the velocity field of the scalar field of applicating fluid, vector field characteristic and vortex flow, pressure field, temperature field and energy field effect, in the firing chamber, build a stable vortex flow field, make the incident air-flow identical with the vortex flow vector, feed the stream of emanating and be lower than the back pressure of first dynamic head value of static pressure, induce the medium of relatively low pressure to enter the firing chamber; The eddy combustion chamber that the utility model is released is used above-mentioned effect (method two, three) and Rafael nozzle critical effect exactly, realizes the changeable burning heat absorption in firing chamber and mixes heat exchange of flash evaporation.It is not enough only making the pressure ratio of the approaching average endothermic temperature correspondence of pressure of medium, at the first-elected turbocharger of the utility model, the eddy combustion chamber, in revolving combustor and the vortex venting gas appliance, scalar field at fluid, the velocity field of vector field characteristic and vortex flow, pressure field, temperature field and energy field effect, under potential barrier stack and the effect of Rafael nozzle critical effect, can dynamically compress with the interior of medium, realize the lifting of pressure medium, make the pressure of medium exceed the pressure ratio of average endothermic temperature correspondence, realize the permanent continuous-flow of medium simultaneously, finally realize degree of depth enthalpy drop.

The theoretical support is summarized as follows with discussion: the place that the macroscopic motion fluid is different from stationary fluid is, the pressure (stagnation pressure) of any point place fluid in the stationary fluid, on all directions, all equate (the scalar field characteristic of fluid), the macroscopic motion fluid not only has the scalar field characteristic, also has the vector field characteristic simultaneously; The macroscopic motion fluid acts on the pressure of observation station, equals the cosine of this direction and direction vector angle and the product of dynamic head, adds the static pressure head value; Promptly

Observation station is in face of coming flow path direction, a=0, and cos a=1, What respond to is the total head (equaling static pressure head and dynamic head sum) of fluid; Perpendicular to fluid vectors line observation station, a=90 °, cos=0, p=p ₁, induction be the static pressure head value p of fluid ₁Fluid incoming flow direction observation point dorsad, a=180 °, cos a=-1,

The pressure of induction equals opposite number that the hydrostatic pressure head value adds the dynamic head value, and (ρ is the proportion of fluid, and w is the speed of fluid, p ₁Be the static pressure head of fluid).

Vortex flow has its unique characteristic again, and the outer gesture of desirable, malleation is strong, and the fundamental characteristics of vortex flow is a retentivity; The velocity field that semo-infinite stretching, extension vortex is induced is by formula

(Г is a voorticity, and h is the perpendicular distance of the interior any point m of vortex to center of vorticity) distributes; The velocity field that unlimited stretching, extension vortex is induced is by formula

Distribute; The scroll compression field of force is by formula

p _c=p _∞-ρ w ²(P distributes _∞Be pressure medium, angle c is the center of vorticity parameter).More than be like velocity field and the vortex flow internal pressure field pattern formula of solid Rotary District in the vortex to annular space vortex flow between the vortex flow boundary layer.In other words, the vortex flow system pressure drop, be directly proportional with the quadratic power of linear velocity, vortex center is like the dynamic head value of solid Rotary District pressure ratio like the low twice of pressure of solid Rotary District annular space between the vortex flow boundary layer, infinitely stretches velocity field that vortex induces and doubles semo-infinite and stretch the velocity field that vortex is induced; Again according to the potential barrier superposition theorem, " superposeing, two or more flow to form new compound flowing; expect this compound mobile stream function or potential function; as long as each original mobile stream function or potential function simply algebraic addition get up just passable " (China Machine Press in 1986, Zheng is in harmony Yu, Lu Zhongqi and edits " fluid mechanics ", 233 pages); The potential barrier superposition theorem of fluid also can be referred to as fluid potential barrier synergistic effect.Real fluid is owing to exist viscosity, " passing in time, velocity circulation will change, that is to say to produce or eliminate vortex, when

The time, Г increases, and vortex flux increases; When The time, Г reduces, and vortex flux reduces " (August nineteen eighty-two, the BJ University Press published, Wu Wangyi work " fluid mechanics " first volume, the 219th page).In vortex flow, because the velocity field of vortex, pressure field and temperature field exist, to prolong involute approaching to vortex center along with fluid particle m, and according to principle of conservation of momentum, liquid speed will increase, suc as formula

Shown in, liquid speed increases the next interior energy to fluid of its energy, can will be converted into kinetic energy in the segment fluid flow, and the fluid temperature (F.T.) of energy level will descend in characterizing,

(k is an adiabatic index, and subscript 0 is an initial parameters) is when fluid particle enters like the solid Rotary District, the speed of fluid descends, and at the w=0 of center of vorticity place, the part kinetic energy of fluid will be converted into the potential energy (potential energy) of fluid, the stagnation of fluid is pressed and will be raise, and the back pressure that acts on the incident air-flow then descends.Turbocharger, eddy combustion chamber and vortex venting gas appliance that the utility model is released all are to seal collar vortex voluntarily, collar vortex scroll end-to-end, belong to the unlimited vortex that stretches, it is comparatively desirable vortex, in vortex effect is under velocity field, pressure field, temperature field and the energy field effect and potential barrier synergistic effect and the effect of Rafael nozzle critical effect of vortex flow, the stagnation that characterizes the medium of scalar field characteristic is pressed and will be raise, and characterizes the vector field characteristic action and then descends in the back pressure of incident air-flow.Follow principle of conservation of momentum, air-flow prolongs constant speed volute involute annular inlet passageway and enters turbocharger, eddy combustion chamber and vortex venting gas appliance, gas flow rate will increase, temperature descends, can change the kinetic energy of gas in the part of gas earlier into, descend like solid Rotary District airspeed in vortex flow, reduce to zero in center of vorticity speed, the kinetic energy of gas changes the potential energy of gas again into, realizes dynamic compression, promptly with the interior pressure that can improve medium of medium, the stack of a plurality of said apparatus effects, make the pressure of medium exceed the corresponding specific pressure of the average endothermic temperature of medium, and then in ensuing bloating plant, realize degree of depth enthalpy drop.Described degree of depth enthalpy drop means the increase of enthalpy when the decline of medium enthalpy in exothermic process is absorbed heat greater than described medium.Certainly having the people whether this to be followed the second law of thermodynamics queries; Any theory all has its Applicable scope, and the second law of thermodynamics is no exception; The just aspect rule of the motion of matter that the second law of thermodynamics discloses, entropy increases, and it all is with good conditionsi that entropy reduces, in general, entropy increases on the prevailing aspect of material in repulsion field, and entropy then reduces on gravity field is occupied an leading position aspect of material; We exist and we common what see is a prevailing aspect of material world, repulsion field, the motion of matter comprises that arrow of time all points to entropy and increases at this level; Make the material entropy minimizing of this aspect or make isentropic motion, must constantly inject energy to system; This aspect of material is to act as feature between big molecule of molecule and micel, is a prevailing world, repulsion field; But this also is not precluded within on this aspect of material, has the prevailing regional area of gravity field, and vortex flow is a kind of low voltage control district, and the negative pressure field of force and gravity field have equivalence.

The beneficial effects of the utility model are: one, in eddy combustion chamber and revolving combustor, velocity field in vortex flow, pressure field, the temperature field, the energy field effect, the scalar field of potential barrier synergistic effect and fluid, under the pumping over check effect effect of vector field characteristic and moving blades, advance in eddy combustion chamber and revolving combustor, under the Rafael nozzle critical effect effect that the throat section that position variant wedge-like body regulating controller of installing on the exhaust passage or deformation formula wedge-like body regulating controller structure shape line are constituted is adjustable, in the permanent continuous-flow of medium, in air fuel mixed combustion process, produce changeable effect, when the temperature of medium raises, pressure gets a promotion synchronously, realize that thermomechanics is referred to as change of state changeable or in many ways, it is advantageous that the pressure ratio of the comparatively approaching average endothermic temperature correspondence of pressure that makes medium, can realize the higher effective enthalpy drop and the thermal efficiency.Two, mixing exhaust section at eddy combustion chamber and revolving combustor, under the changeable state of same permanent Continuous Flow, allow and directly contact with the high-temperature fuel gas air mixture through an amount of high-pressure atomization clean water fine drop surface of preheating, atomizing clean water pressure descends suddenly, make the clean water atomizing trickleer, simultaneous temperature raises suddenly, rapid flash vaporization mixed heat transfer, this is that a kind of nothing defines the heat exchange that heat transfer surface does not have the temperature difference, heat transfer surface is exactly atomized water fine drop surface, the gas-air water vapor tends to same temperature, its efficient and thermal conduction rate be other any heat transmission equipment and heat exchange mode can't than like, the gas-air water vapor mixture that produces, temperature descends significantly, the parts that contact with medium can adopt conventional heat-resistant material production, and pressure gets a promotion, and make the further approaching on average pressure ratio of endothermic temperature correspondence of pressure of medium; Reduced the use amount of oozing the cold compression air, can adopt lower excess air coefficient, the corresponding gas compressor load of should reducing, and the content of NOx in the weary gas of corresponding minimizing, simultaneously clean atomized water also can in and part harmful gas in the combustion gas, reduce pollution to environment.Three, medium enters turbocharger along constant speed volute involute shape gas-entered passageway, eddy combustion chamber and vortex venting gas appliance, because momentum conservation, can change the kinetic energy of medium in the part of medium earlier into, in this device, form stable vortex flow field, velocity field in vortex flow, pressure field, the temperature field, under energy field effect and the effect of potential barrier synergistic effect, advance at this device simultaneously, under the Rafael nozzle critical effect effect that the throat section that position variant wedge-like body regulating controller of installing on the exhaust passage or deformation formula wedge-like body regulating controller structure shape line are constituted is adjustable, the long-pending potential barrier stack of the MEDIA FLOW coil of wire, medium is dynamically compressed, this kinetic energy further changes the potential energy of medium into, and pressure medium gets a promotion.The stack of the said apparatus effect of series connection, make the pressure of medium exceed the pressure ratio of average endothermic temperature correspondence, realize the permanent continuous-flow of medium simultaneously, realize degree of depth enthalpy drop for vortex combustion and steam turbine and lay the foundation, opened up new way for improving efficiency of heat engine and new energy development.Four, cover shaft type differential coupling is by its planetary self adaption differential rotation, realize that each inserts the self adaption dynamic adjustments of axle revolution and enthalpy drop, solved output of long-term puzzlement power circle multi power source dynamic unity and many group turbines and other power plant enthalpy drop dynamic assignment problem; Two input shafts of cover shaft type differential coupling (being intermediate pressure turbine axle and cover shaft type low pressure turbine axle) when the unpowered input of a side, can be prevented reversing automatically.Five, position variant wedge-like body regulating controller and deformation formula wedge-like body regulating controller have to regulate and control to be easy to realize, flow resistance is little, sew few characteristics.Six, the utlity model has that reasonable in design, environmental pollution are little, heat exchange efficiency and speed height, the thermal efficiency and overall efficiency height, comprehensive economy are better than gas turbine and the steam turbine used at present.

Description of drawings

Fig. 1 is the axial section schematic representation that adopts the vortex combustion and steam turbine of grade separation type eddy combustion chamber 93; Fig. 2 is the axial section schematic representation that adopts the vortex combustion and steam turbine of override type eddy combustion chamber 97; Fig. 3 is the axial section schematic representation that adopts the vortex combustion and steam turbine of tubular revolving combustor 54; Fig. 4 is the axial section schematic representation that adopts the vortex combustion and steam turbine of ring rotation firing chamber 71; Fig. 5 is the A-A generalized section of Fig. 4; Fig. 6 is the B-B generalized section of Fig. 1; Fig. 7 is the C-C generalized section of Fig. 2; Fig. 8 is the D-D generalized section of Fig. 3; Fig. 9 is the structural representation in tangential slit; Figure 10 is vortex venting gas appliance 53 side-looking generalized sections; Figure 11 is a structural representation of variant wedge-like body regulating controller 3; Figure 12 is mounted in the structural representation of the deformation formula wedge-like body regulating controller 4 on the air-flow path between the comb of blade-shaped pipe; Figure 13 is mounted in the structural representation of the deformation formula wedge-like body regulating controller 4 on annular or the rectangle air-flow path; Figure 14 is the structural representation of the automatic anti-reverse-rotation device of differential coupling; Figure 15 is the J-J generalized section of Figure 14; Figure 16 is the structural representation of revolving combustor burner inner liner lamination interlayer aperture; Figure 17 is the G-G generalized section of Figure 16.

What need indicate a bit is: be limited to page size, the multistage turbocharger of first group of series connection only shows 2, the second groups of multistage turbochargers of connecting of one-level grade separation type turbocharger and only shows secondary grade separation type turbocharger 2 among Fig. 1, Fig. 3, Fig. 4; Among Fig. 2 the multistage turbocharger of first group and second group series connection each only show three grades of override type turbochargers 20, the multistage turbocharger of the 3rd group of series connection among Fig. 1, Fig. 2, Fig. 3 and Fig. 4 and the multistage turbocharger of the 4th group of series connection all only show one-level grade separation type turbocharger 2, in order to reach higher pressure medium, be not limited to the progression of turbocharger shown in the accompanying drawing in practicing.

Embodiment

Embodiment one: in conjunction with Fig. 1～Figure 17 present embodiment is described, described vortex combustion and steam turbine comprises Starter 55, Starter clutch 56, gas compressor 1, firing chamber, ratchet type overrunning clutch 57, cover shaft type differential coupling 10, high pressure turbine 7, intermediate pressure turbine 8 and low pressure turbine 14; It is characterized in that: described vortex combustion and steam turbine also comprises turbocharger, vortex venting gas appliance 53, solid-liquid body segregating unit, wedge-like body regulating controller; Described turbocharger is made up of the first group of multistage turbocharger of connecting and second group of multistage turbocharger of connecting of 7 settings in firing chamber and high pressure turbine, the 3rd group of multistage turbocharger of connecting of 8 settings of high pressure turbine 7 and intermediate pressure turbine, the 4th group of multistage turbocharger of connecting of 14 settings of intermediate pressure turbine 8 and low pressure turbine that are arranged between gas compressor 1 and firing chamber; Be respectively arranged with a wedge-like body regulating controller on the inlet and outlet passage of described turbocharger and firing chamber, first order turbocharger and vortex venting gas appliance 53 in the multistage turbocharger of every group of series connection are provided with a solid-liquid body segregating unit; Solid-liquid body segregating unit is respectively the first solid-liquid body segregating unit 121, the second solid-liquid body segregating unit 131 and the 3rd solid-liquid body segregating unit 141, and the first solid-liquid body segregating unit 121, the second solid-liquid body segregating unit 131 are identical with the 3rd solid-liquid body segregating unit 141 structures;

The Starter output shaft 65 of Starter 55 is in transmission connection by the end of Starter clutch 56 with the compressorshaft 58 of gas compressor 1, and an end of the high pressure turbine axle 6 of high pressure turbine 7 is in transmission connection by the other end of ratchet type overrunning clutch 57 with the compressorshaft 58 of gas compressor 1; The cover shaft type low pressure turbine axle 13 of the intermediate pressure turbine axle 9 of intermediate pressure turbine 8 and low pressure turbine 14 is affixed with two taper driving gears 24 of cover shaft type differential coupling 10 respectively, and power is by stub 16 outputs of cover shaft type differential coupling 10; The connection of joining of the annular waste air duct of gas compressor 1 and the annular inlet passageway of first group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of first group of series connection is joined with the annular inlet passageway of firing chamber and is communicated with, the connection of joining of the annular waste air duct of firing chamber and the annular inlet passageway of second group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of second group of series connection is joined with the annular inlet passageway of high pressure turbine 7 and is communicated with, the connection of joining of the annular waste air duct of high pressure turbine 7 and the annular inlet passageway of the 3rd group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of the 3rd group of series connection is joined with the annular inlet passageway of intermediate pressure turbine 8 and is communicated with, the connection of joining of the annular waste air duct of intermediate pressure turbine 8 and the annular inlet passageway of the 4th group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of the 4th group of series connection is joined with the annular inlet passageway of low pressure turbine 14 and is communicated with, the annular waste air duct of low pressure turbine 14 is joined with the annular inlet passageway of vortex venting gas appliance 53 and is communicated with, and the relief opening of vortex venting gas appliance 53 is communicated with atmosphere.

Burning heat absorption under the mixed combustion section air of firing chamber and the changeable state of fuel in permanent continuous vortex flow; Under same changeable state, high-temperature fuel gas air mixture and an amount of high-pressure atomization clean water fine drop surface directly contact the flash vaporization mixed heat transfer in firing chamber mixing exhaust section; In described turbocharger, eddy combustion chamber and vortex venting gas appliance, medium is dynamically compressed in permanent continuous vortex flow, can change the kinetic energy of medium in the part of medium earlier into, and kinetic energy changes the potential energy of medium again into; Cover shaft type differential coupling 10 carries out the self adaption dynamic adjustments by the differential rotation of cover shaft type differential coupling planetary pinion 12 to each access axle revolution and enthalpy drop; Two input shafts of described cover shaft type differential coupling when the unpowered input of a side, can be prevented reversing automatically; Described vortex combustion and steam turbine all devices is by a computer regulating center and a plurality of execution and the unified control of servomechanism.

Described turbocharger is grade separation type turbocharger 2 or override type turbocharger 20; Described wedge-like body regulating controller is a variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4; Described firing chamber is grade separation type eddy combustion chamber 93 or override type eddy combustion chamber 97, or ring rotation firing chamber 71 or tubular revolving combustor 54; Can develop multi-series vortex combustion and steam turbine according to general plotting of the present utility model.

Embodiment two: present embodiment is described in conjunction with Fig. 1～Fig. 4 and Figure 11, the wedge-like body regulating controller of present embodiment is a variant wedge-like body regulating controller 3, position variant wedge-like body regulating controller 3 by position variant wedge-like body regulating controller runner 31, two connecting rods 33, a plurality of movable wedge-like body 30, at least two group position variant wedge-like body regulating controller slideways 32, at least two rooted tooth wheel shafts 19, at least four gears 39 and at least four toothed rack 34, form; Both quantity of gear 39 and tooth bar 34 is identical, adjacent two toothed rack 34 be arranged in parallel, be packed in respectively on corresponding two connecting rods 33, correspondingly on every rooted tooth wheel shaft 19 install two gears 39, every toothed rack 34 and an adjacent gear 39 engagements, gear shaft 19 and gear 39 are rotatable components, two 33 on connecting rods are fixed with a plurality of movable wedge-like bodys 30, a plurality of movable wedge-like body 30 spaced sets, adjacent two movable wedge-like bodys 30 are for be arrangeding in parallel, the movable wedge-like body 30 of corresponding position variant wedge-like body regulating controller slideway 32 is provided with chute, be slidingly matched with at least two group position variant wedge-like body regulating controller slideways 32 by chute connecting rod 33 and a plurality of movable wedge-like body 30, movable wedge-like body 30 has a continuous points of tangency and corresponding with position variant wedge-like body regulating controller runner 31; Every group of position variant wedge-like body regulating controller slideway 32 is two, installs respectively on the variant wedge-like body regulating controller runner 31 corresponding two parallel walls on the throne, and two adjacent groups position variant wedge-like body regulating controller slideway 32 be arranged in parallel.Other is identical with embodiment one.

Both quantity of the gear 39 of present embodiment and tooth bar 34 is identical, be preferably a twice of variant wedge-like body regulating controller slideway 32 quantity, the quantity of gear 39 and tooth bar 34 was at least four when position variant wedge-like body regulating controller runner 31 was rectangle, and its quantity was at least six when a position variant wedge-like body regulating controller runner 31 was annular; The gear shaft 19 of position variant wedge-like body regulating controller is driven by servomechanism, engagement by gear 39 and tooth bar 34 drives two connecting rods 33 respectively and synchronously, described connecting rod 33 drives movable wedge-like body 30 along position variant wedge-like body regulating controller slideway 32 directed displacements, movable wedge-like body 30 shape lines constitute the adjustable Rafael nozzle in throat section with position variant wedge-like body regulating controller runner 31 continuous phase point of contact structure shape lines, described Rafael nozzle throat section minimum when the continuous phase point of contact is tangent, thereby can make things convenient for regulation and control rate-of flow and upstream pressure chamber pressure under threshold state in real time, its action principle is that volume flow keeps and pressure wave check effect under the Rafael nozzle threshold state; Movable wedge-like body 30 is that blade-shaped also can be other any body.

Embodiment three: in conjunction with Fig. 1～Fig. 4, Figure 12 and Figure 13 present embodiment is described, the deformation formula wedge-like body regulating controller 4 of present embodiment by deformation formula wedge-like body regulating controller runner 110, a plurality of roller 36, a plurality of deformable wedge-like body 37, organize deformation formula wedge-like body regulating controller slideway 77, a plurality of adjusting axle 38 and a plurality of regulating wheel 35 more and form; Many group deformation formula wedge-like body regulating controller slideways 77 are installed on the deformation formula wedge-like body regulating controller runner 110 corresponding two parallel walls, and two adjacent groups deformation formula wedge-like body regulating controller slideway 77 be arranged in parallel; Each deformable wedge-like body 37 is made up of two spring steel plates, the two ends Joint of two spring steel plates, one end of each deformable wedge-like body 37 is packed on two walls of deformation formula wedge-like body regulating controller runner 110 correspondences, and the other end of each deformable wedge-like body 37 is installed on the corresponding deformation formula wedge-like body regulating controller slideway 77 and can slides along its orientation; Regulating wheel 35 is oval wheel shape member, and the two ends of each regulating wheel 35 are equipped with roller 36, and regulating wheel 35 is packed on the adjusting axle 38 and between two spring steel plates of each deformable wedge-like body 37, adjusting axle 38 is a rotatable components; Deformation formula wedge-like body regulating controller runner 110 is annular air-flow path, rectangle air-flow path or the comb air-flow path that is provided with the blade-shaped pipe, a plurality of deformable wedge-like bodys 37 are set in qually spaced on annular air-flow path or the rectangle air-flow path, perhaps are separately positioned between the comb of the blade-shaped pipe on the blade-shaped pipe comb air-flow path.Other is identical with embodiment one.

Deformable wedge-like body 37 in the present embodiment, deformation formula wedge-like body regulating controller slideway 77, adjusting axle 38 are all identical with regulating wheel 35 4 quantity, every group of deformation formula wedge-like body regulating controller slideway 77 is two, is installed in respectively on the deformation formula wedge-like body regulating controller runner 110 corresponding two parallel walls; Drive adjusting axle 38 by servomechanism, adjusting axle 38 drives regulating wheel 35 and rotates, regulating wheel 35 is by two spring steel plates of roller 36 at medial support deformable wedge-like body 37, make it produce distortion, when the major axis of regulating wheel 35 and MEDIA FLOW line parallel (Figure 12), the runner equivalent section maximum that deformable wedge-like body structure shape line is constituted, when the major axis of regulating wheel 35 is vertical with streamline (Figure 13), the cross section of fluid channel minimum, deformable wedge-like body structure shape line constitutes Rafael nozzle throat equivalent section in the runner on the cross section of regulating wheel 35 correspondences; Deformation formula wedge-like body regulating controller runner 110 is annular or rectangle air-flow path, it also can be the comb air-flow path that is provided with the first blade-shaped pipe 92 or the second blade-shaped pipe 115, on annular or rectangle air-flow path, be fit to adopt structure shown in Figure 13, deformable wedge-like body 37 equidistantly is installed in annular or the rectangle air-flow path, when in deformation formula wedge-like body regulating controller runner 110, being provided with the comb of the first blade-shaped pipe 92 or the second blade-shaped pipe 115, can adopt structure shown in Figure 12, deformable wedge-like body 37 is installed in respectively between the first blade-shaped pipe 92 or the second blade-shaped pipe 115; Deformable wedge-like body 37 is that blade-shaped also can be other any body.

Embodiment four: in conjunction with Fig. 1～Fig. 4, Figure 14 and Figure 15 present embodiment is described, the cover shaft type differential coupling 10 of present embodiment is made up of cross axle 11, stub 16, cross axle scaffold 23, differential coupling housing 5, four planetary pinions 12, two taper driving gears 24, four bearings 60 and two automatic anti-reverse-rotation devices of differential coupling; Four planetary pinion 12 rotatable being installed in respectively on the cross axle 11, it is affixed with the middle part of cross axle 11 that one end of stub 16 passes cover shaft type low pressure turbine axle 13, cross axle 11 is packed on the cross axle scaffold 23, cross axle scaffold 23 is by two bearings, 60 rotatable being installed in respectively on intermediate pressure turbine axle 9 and the cover shaft type low pressure turbine axle 13, intermediate pressure turbine axle 9 and cover shaft type low pressure turbine axle 13 are packed in respectively on the corresponding taper driving gear 24, and two taper driving gears 24 are meshed with four planetary pinions 12 respectively; The automatic anti-reverse-rotation device of differential coupling is made up of wheel disc 105, support 104, two axle keys 106, a plurality of wedge shape raceway 107, a plurality of spring 102 and a plurality of balls 103; One end of intermediate pressure turbine axle 9 and cover shaft type low pressure turbine axle 13 is contained in respectively in the central shaft hole of the center hole of support 104 and wheel disc 105, and it is affixed by an axle key 106 and wheel disc 105 respectively, intermediate pressure turbine axle 9 and cover shaft type low pressure turbine axle 13 respectively are rotationally connected by a bearing 60 and support 104, support 104 and differential coupling housing 5 Joints, wheel disc 105 is processed with a plurality of wedge shape raceways 107 with its circumferencial direction of upper edge, support 104 an adjacent side end face, a ball 103 and a spring 102 are housed in each wedge shape raceway 107, and described spring 102 is arranged on the outside of ball 103.

When planetary pinion 12 and taper driving gear 24 diameters hour, cross axle 11 can not be installed on the cross axle scaffold 23, and saves cross axle scaffold 23 and two bearings; Also can adopt two or three planetary pinions to make cover shaft type differential coupling 10 designs simplifications.Intermediate pressure turbine axle 9 and cover shaft type low pressure turbine axle 13 are wherein during any unpowered output, the automatic anti-reverse-rotation device spring 102 of this side promotes ball 103 and enters wedge shape raceway 107, ball 103 blocks support 104 and wheel disc 105 in wedge shape raceway 107, make it can not reverse rotation, anti-automatically the reverse; Owing to centrifugal action, ball 103 pressure springs 102 break away from wedge shape raceways 107, do not produce abrasion when each unit normal run; Described ball 103 can be substituted by roller.Transmission is in proper order: intermediate pressure turbine axle 9 drives 24 rotations of two taper driving gears with cover shaft type low pressure turbine axle 13 with different revolutions, two taper driving gear 24 engagement driving planetary pinions 12 are done the differential rotation, planetary pinion 12 promotes cross axle 11 rotations, cross axle 11 drives stub 16 and cross axle scaffold 23 rotates together, and torque is by stub 16 outputs.Cover shaft type differential coupling 10 can be realized diaxon and dynamically connect (three and when connecting with last axle with last axle differential, next stage cover shaft type differential coupling is a side input shaft with upper level sleeve formula differential coupling output shaft stub), allow each to insert axle with different revolution runnings, in a power system, differential rotation by planetary pinion 12 realizes that each inserts self adaption dynamic differential adjusting of axle revolution, but each inserts the enthalpy drop of axle power plant dynamic assignment, effectively reduces the leaving loss of power plant.

Embodiment five: in conjunction with Fig. 1～Fig. 4, Fig. 9, Figure 10 present embodiment is described, the vortex venting gas appliance 53 of present embodiment is made of suction port 51, vortex venting gas appliance external admission mouth 50, vortex venting gas appliance relief opening 48, the 3rd solid-liquid body segregating unit 141, air guide volute 78 and strut 108 in vortex venting gas appliance gas-entered passageway 126, vortex venting gas appliance air inlet section 73, vortex venting gas appliance changeover portion 80, vortex venting gas appliance exhaust section 163, the vortex venting gas appliance; The 3rd solid-liquid body segregating unit 141 also comprises the 3rd tangential slit 174, the 3rd gas backstreaming pipe 175 and the 3rd solid-liquid body discharge tube 176; Vortex venting gas appliance air inlet section 73 is the annular constant speed volutes of two inlets, air guide volute 78 is divided into two the suction port of vortex venting gas appliance air inlet section 73, and be respectively suction port 51 and vortex venting gas appliance external admission mouth 50 in the vortex venting gas appliance, vortex venting gas appliance external admission mouth 50 is positioned at the outside of vortex venting gas appliance suction port 51, suction port 51 and vortex venting gas appliance external admission mouth 50 is all annular and join with the vortex venting gas appliance gas-entered passageway 126 of annular and to be communicated with in the vortex venting gas appliance, the inner edge of vortex venting gas appliance gas-entered passageway 126 is an involute shape and tangentially external with vortex venting gas appliance air inlet section 73 volutes, and the outside of vortex venting gas appliance gas-entered passageway 126 is prolongation transition wires of vortex venting gas appliance air inlet section 73 volute involutes; Air guide volute 78 is arranged on the centre of interior suction port 51 of vortex venting gas appliance and vortex venting gas appliance external admission mouth 50, and air guide volute 78 is supported by strut 108 and be affixed with vortex venting gas appliance air inlet section 73 volutes, and the cross section of strut 108 is a blade-shaped; Vortex venting gas appliance changeover portion 80 is two Cylinder shape constructional elements, one end of two Cylinder shape constructional elements respectively with vortex venting gas appliance air inlet section tangent connection of 73 volutes, air guide volute 78 and vortex venting gas appliance air inlet section 73 volutes that vortex venting gas appliance changeover portion 80 is corresponding with vortex venting gas appliance air inlet section 73 tangent places are save; The volute of vortex venting gas appliance exhaust section 163 is half toroidal, the other end of two Cylinder shape constructional elements of vortex venting gas appliance changeover portion 80 joins with two end faces of the hemicycle of vortex venting gas appliance exhaust section 163 annular volute respectively and is communicated with, vortex venting gas appliance exhaust section 163 is made up of ring 49 and the adjustable outer shroud 47 of vortex venting gas appliance in the vortex venting gas appliance, the vortex venting gas appliance is adjustable, and outer shroud 47 is arranged on the outside of ring 49 in the vortex venting gas appliance, array-type is provided with a plurality of vortex venting gas appliance relief openings 48 on interior ring 49 of vortex venting gas appliance and adjustable outer shroud 47 opposite positions of vortex venting gas appliance, and the vortex venting gas appliance is adjustable, and the interior ring 49 of outer shroud 47 relative vortex venting gas appliance is slidingly matched vertically; Tangent the 3rd tangential slit 174 that is provided with a plurality of contrary airflow directions on the vortex venting gas appliance air inlet section 73 volute toroidal shells, the 3rd tangential slit 174 tangentially is communicated with the 3rd solid-liquid body segregating unit 141, the 3rd solid-liquid body segregating unit 141 is ring housing structures, and a side that is arranged on vortex venting gas appliance air inlet section 73 volute toroidal shells is also mutually circumscribed; The 3rd gas backstreaming pipe 175 is made up of the comb of a plurality of the 5th blade-shaped pipes 118 of equidistant arrangement, be installed on the 3rd solid-liquid body segregating unit 141 toroidal shells, the one end extend into the center of the 3rd solid-liquid body segregating unit 141, the other end on the air-flow sense of rotation with the vortex venting gas appliance air inlet section 73 volutes UNICOM of tangentially joining; The 3rd solid-liquid body discharge tube 176 tangentially is installed on the 3rd solid-liquid body segregating unit 141 toroidal shells, and direction tangential is tangential opposite on the 3rd solid-liquid body segregating unit 141 toroidal shells with the 3rd tangential slit 174.Other is identical with embodiment one, two or three.

The adjustable outer shroud 47 of the vortex venting gas appliance of present embodiment is driven by servomechanism, and the interior ring of its relative vortex venting gas appliance 49 positions are changed, and can make things convenient for the size of adjusting vortex venting gas appliance relief opening 48 equivalent sections in real time.Weary gas forms a circular collar vortex in the air inlet section, and tangential external changeover portion exhaust section forms an approximate ellipsoidal collar vortex again, and two collar vortexs are overlapped, and mutually promote.The 3rd solid-liquid body segregating unit 141 centers comparatively clean gas are recycled in the vortex venting gas appliance 53 by the 3rd gas backstreaming pipe 175, isolate the solid-liquid body and are discharged by the 3rd solid-liquid body discharge tube 176; Arrow points is an airflow direction among Fig. 9.

Embodiment six: present embodiment is described in conjunction with Fig. 1～Fig. 5 and Fig. 9 and Figure 11～Figure 13, the turbocharger of present embodiment is a grade separation type turbocharger 2, and grade separation type turbocharger 2 is made up of grade separation type turbocharger volute 129, grade separation type turbocharger suction port 45, grade separation type turbocharger relief opening 46, the first solid-liquid body segregating unit 121, grade separation type turbocharger gas-entered passageway 159 and grade separation type turbocharger exhaust passage 160; The first solid-liquid body segregating unit 121 also comprises the first tangential slit 125, the first gas backstreaming pipe 124 and the first solid-liquid body discharge tube 123; Grade separation type turbocharger volute 129 is annular constant speed volutes, grade separation type turbocharger suction port 45 and grade separation type turbocharger gas-entered passageway 159 are all annular and are connected, the inner edge of grade separation type turbocharger gas-entered passageway 159 is an involute shape and tangentially external with grade separation type turbocharger volute 129, and the outside of grade separation type turbocharger gas-entered passageway 159 is prolongation transition wires of grade separation type turbocharger volute 129 involutes; Grade separation type turbocharger relief opening 46 is made up of the comb of the first blade-shaped pipe 92 of a plurality of equidistant arrangements, and the comb of the first blade-shaped pipe 92 of a plurality of equidistant arrangements is installed on the toroidal shell of grade separation type turbocharger volute 129; Grade separation type turbocharger gas-entered passageway 159 is crossed in grade separation type turbocharger exhaust passage 160, grade separation type turbocharger gas-entered passageway 159 and grade separation type turbocharger exhaust passage 160 are provided with a solid and intersect section, being arranged in the comb of the first blade-shaped pipe 92 of three-dimensional a plurality of equidistant arrangements of intersecting the section place is grade separation type turbocharger exhaust passage 160, and the comb that is arranged on the first blade-shaped pipe 92 of three-dimensional a plurality of equidistant arrangements of intersecting section is outward a grade separation type turbocharger gas-entered passageway 159; The comb of the first blade-shaped pipe 92 of grade separation type turbocharger relief opening 46 annular spaced sets joins with the grade separation type turbocharger exhaust passage 160 of annular and is communicated with; Be respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 on grade separation type turbocharger gas-entered passageway 159 and the grade separation type turbocharger exhaust passage 160; With the grade separation type turbocharger volute 129 tangent first tangential slits 125 that are provided with a plurality of contrary airflow directions, the first tangential slit 125 tangentially joins with the first solid-liquid body segregating unit 121 and is communicated with, the first solid-liquid body segregating unit 121 is ring housing structures, and a side that is arranged on grade separation type turbocharger 2 is also mutually circumscribed; The first gas backstreaming pipe 124 is made up of the comb of the 3rd blade-shaped pipe 116 of a plurality of equidistant arrangements, be installed on the first solid-liquid body segregating unit, 121 toroidal shells, the one end extend into the center of the first solid-liquid body segregating unit 121, the other end on the air-flow sense of rotation with grade separation type turbocharger volute 129 UNICOM of tangentially joining, the first solid-liquid body discharge tube 123 tangentially is installed on the first solid-liquid body segregating unit, 121 toroidal shells, and direction tangential is tangential opposite on the first solid-liquid body segregating unit, 121 toroidal shells with the first tangential slit 125.Other is identical with embodiment one, two or three.

The comb of the first blade-shaped pipe 92 on the grade separation type turbocharger exhaust passage 160 stretches into certain-length in the grade separation type turbocharger volute 129, prevents that the solid-liquid body enters the exhaust passage in the medium; The first solid-liquid body segregating unit, 121 centers comparatively clean gas are recycled in the turbocharger by the first gas backstreaming pipe 124, isolate the solid-liquid body and are discharged by the first solid-liquid body discharge tube 123.When medium is clean gas, do not establish the first solid-liquid body segregating unit 121, at this moment the comb of the first blade-shaped pipe 92 of grade separation type turbocharger relief opening 46 then with the 129 tangent settings of grade separation type turbocharger volute.Grade separation type turbocharger exhaust passage 160 carries out the transition to ring pipe by the first blade-shaped pipe, 92 combs, changeover portion flaring structure shape line, be convenient to adopt position variant wedge-like body regulating controller 3, the grade separation type turbocharger 2 three-dimensional combs that intersect the first blade-shaped pipe 92 of section are outward grade separation type turbocharger gas-entered passageways 159, the Rafael nozzle shape air-flow path of flaring behind the first convergent of formation is convenient to adopt position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 equally on adjacent two first blade-shaped pipes, the 92 structure shape line intake ducts.

Embodiment seven: present embodiment is described in conjunction with Fig. 2, Fig. 7, Fig. 9 and Figure 11～Figure 13, the turbocharger of present embodiment is an override type turbocharger 20, and override type turbocharger 20 is made up of override type turbocharger volute 130, override type turbocharger suction port 72, override type turbocharger relief opening 66, the second solid-liquid body segregating unit 131, override type turbocharger gas-entered passageway 161 and override type turbocharger exhaust passage 162; The second solid-liquid body segregating unit 131 also comprises the second tangential slit 171, the second gas backstreaming pipe 172 and the second solid-liquid body discharge tube 173; Override type turbocharger volute 130 is annular constant speed volutes, override type turbocharger gas-entered passageway 161 and override type turbocharger suction port 72 are all annular and are connected, the inner edge of override type turbocharger gas-entered passageway 161 is an involute shape and tangentially external with override type turbocharger volute 130, and the outside of override type turbocharger gas-entered passageway 161 is prolongation transition wires of override type turbocharger volute 130 involutes; Override type turbocharger relief opening 66 is made up of the comb of the second blade-shaped pipe 115 of a plurality of equidistant arrangements, and the comb of the second blade-shaped pipe 115 of a plurality of equidistant arrangements is installed on override type turbocharger volute 130 toroidal shells; The comb of the second blade-shaped pipe 115 of override type turbocharger relief opening 66 annular spaced sets joins with the override type turbocharger exhaust passage 162 of annular and is communicated with, and is respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 on override type turbocharger exhaust passage 162 and the override type turbocharger gas-entered passageway 161; With the override type turbocharger volute 130 tangent second tangential slits 171 that are provided with a plurality of contrary airflow directions, the second tangential slit 171 tangentially is communicated with the second solid-liquid body segregating unit 131, the second solid-liquid body segregating unit 131 is ring housing structures, and a side that is arranged on override type turbocharger 20 is also mutually circumscribed; The second gas backstreaming pipe 172 is made up of the comb of the quaterfoil shape pipe 117 of a plurality of equidistant arrangements, be installed on the second solid-liquid body segregating unit, 131 toroidal shells, the one end extend into the center of the second solid-liquid body segregating unit 131, the other end on the air-flow sense of rotation with override type turbocharger volute 130 UNICOM of tangentially joining; The second solid-liquid body discharge tube 173 tangentially is installed on the second solid-liquid body segregating unit, 131 toroidal shells, and direction tangential is tangential opposite on the second solid-liquid body segregating unit, 131 toroidal shells with the second tangential slit 171.Other is identical with embodiment one, two or three.

The comb of the second blade-shaped pipe 115 on the override type turbocharger exhaust passage 162 of present embodiment stretches into certain-length in the override type turbocharger volute 130; The second solid-liquid body segregating unit, 131 centers comparatively clean gas are recycled in the turbocharger by the second gas backstreaming pipe 172, isolate the solid-liquid body and are discharged by the second solid-liquid body discharge tube 173.When medium is clean gas, do not establish the second solid-liquid body segregating unit 131, at this moment the second blade-shaped pipe, 115 combs of override type turbocharger relief opening 66 then with the 130 tangent settings of override type turbocharger volute.Override type turbocharger exhaust passage 162 carries out the transition to ring pipe by the second blade-shaped pipe, 115 combs, changeover portion flaring structure shape line, be convenient to adopt position variant wedge-like body regulating controller 3, when being equipped with turbocharger before the override type turbocharger 20, its gas-entered passageway also can adopt a variant wedge-like body regulating controller 3.

Embodiment eight: present embodiment is described in conjunction with Fig. 1 and Fig. 6 and Figure 11～Figure 13, the firing chamber of present embodiment is grade separation type eddy combustion chamber 93, and grade separation type eddy combustion chamber 93 is by grade separation type eddy combustion chamber volute 132, a plurality of grade separation type eddy combustions chamber dividing plate 100, grade separation type eddy combustion chamber suction port 29, grade separation type eddy combustion chamber relief opening 96, grade separation type eddy combustion chamber exhaust air collecting chamber 94, exhaust passage, grade separation type eddy combustion chamber 95, grade separation type eddy combustion chamber gas-entered passageway 136, at least one first fuel nozzle 133, at least one first igniter 134, at least one first water spout 135 and a plurality of wicker leaf shape pipe 120 are formed; Grade separation type eddy combustion chamber volute 132 is annular constant speed volutes, grade separation type eddy combustion chamber gas-entered passageway 136 and grade separation type eddy combustion chamber suction port 29 are all annular and are connected, the inner edge of grade separation type eddy combustion chamber gas-entered passageway 136 is an involute shape and tangentially external with grade separation type eddy combustion chamber volute 132, and the outside of grade separation type eddy combustion chamber gas-entered passageway 136 is prolongation transition wires of grade separation type eddy combustion chamber volute 132 involutes; Spaced set has a plurality of grade separation type eddy combustions chamber dividing plate 100 in the grade separation type eddy combustion chamber 93, a plurality of grade separation type eddy combustions chamber dividing plate 100 is divided into multistage vertically with grade separation type eddy combustion chamber 93, every section grade separation type eddy combustion chamber 93 is made up of a grade separation type eddy combustion chamber mixed combustion section 90 and a grade separation type eddy combustion chamber mixing exhaust section 91, be provided with at least one first fuel nozzle 133 and at least one first igniter 134 in each grade separation type eddy combustion chamber mixed combustion section 90, be provided with at least one first water spout 135 in each grade separation type eddy combustion chamber mixing exhaust section 91, the centre of each grade separation type eddy combustion chamber dividing plate 100 is equipped with one first dividing plate air passing hole 101, and each section grade separation type eddy combustion chamber 93 forms a collar vortex through the first dividing plate air passing hole, 101 end-to-ends; The collar vortex cross section grade separation type eddy combustion chamber volute 132 of grade separation type eddy combustion chamber 93 is provided with grade separation type eddy combustion chamber relief opening 96, grade separation type eddy combustion chamber relief opening 96 is positioned at the inboard of the grade separation type eddy combustion chamber dividing plate 100 of each grade separation type eddy combustion chamber mixing exhaust section 91 end, the grade separation type eddy combustion chamber volute 132 in relief opening 96 outsides, grade separation type eddy combustion chamber is provided with grade separation type eddy combustion chamber exhaust air collecting chamber 94, grade separation type eddy combustion chamber relief opening 96 is communicated with grade separation type eddy combustion chamber exhaust air collecting chamber 94, grade separation type eddy combustion chamber exhaust air collecting chamber 94 joins with wicker leaf shape pipe 120 and is communicated with, wicker leaf shape pipe 120 joins with the exhaust passage, grade separation type eddy combustion chamber 95 of annular and is communicated with, wicker leaf shape pipe 120 is arranged on the grade separation type eddy combustion chamber volute 132 of grade separation type eddy combustion chamber suction port 29 correspondences, at least one wicker leaf shape pipe 120 is established in every section grade separation type eddy combustion chamber 93, and the outside of wicker leaf shape pipe 120 is grade separation type eddy combustion chamber gas-entered passageways 136; Be respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 on grade separation type eddy combustion chamber gas-entered passageway 136 and the exhaust passage, grade separation type eddy combustion chamber 95.Other is identical with embodiment one, two or three.

Embodiment nine: present embodiment is described in conjunction with Fig. 2 and Fig. 7 and Figure 11～Figure 13, the firing chamber of present embodiment is override type eddy combustion chamber 97, and override type eddy combustion chamber 97 is by override type eddy combustion chamber volute 137, a plurality of override type eddy combustions chamber dividing plate 138, override type eddy combustion chamber suction port 143, override type eddy combustion chamber exhaust air collecting chamber 144, override type eddy combustion chamber relief opening 99, exhaust passage, override type eddy combustion chamber 98, override type eddy combustion chamber gas-entered passageway 166, at least one second fuel nozzle 145, at least one secondary igniter 146 and at least one second water spout 147 are formed; Override type eddy combustion chamber volute 137 is annular constant speed volutes, override type eddy combustion chamber gas-entered passageway 166 and override type eddy combustion chamber suction port 143 are all annular and are connected, the inner edge of override type eddy combustion chamber gas-entered passageway 166 is an involute shape and tangentially external with override type eddy combustion chamber volute 137, and the outside of override type eddy combustion chamber gas-entered passageway 166 is prolongation transition wires of override type eddy combustion chamber volute 137 involutes; Spaced set has a plurality of override type eddy combustions chamber dividing plate 138 in the override type eddy combustion chamber 97, a plurality of override type eddy combustions chamber dividing plate 138 is divided into multistage vertically with override type eddy combustion chamber 97, every section override type eddy combustion chamber 97 is made up of an override type eddy combustion chamber mixed combustion section 140 and an override type eddy combustion chamber mixing exhaust section 142, be provided with at least one second fuel nozzle 145 and at least one secondary igniter 146 in each override type eddy combustion chamber mixed combustion section 140, be provided with at least one second water spout 147 in each override type eddy combustion chamber mixing exhaust section 142, the centre of each override type eddy combustion chamber dividing plate 138 is equipped with a second partition air passing hole 139, and each section override type eddy combustion chamber 97 forms a collar vortex through second partition air passing hole 139 end-to-ends; The position that is shaped as " C " font on the 97 collar vortex cross section override type eddy combustion chamber volutes 137 of override type eddy combustion chamber is provided with override type eddy combustion chamber relief opening 99, override type eddy combustion chamber relief opening 99 is positioned at the inboard of the override type eddy combustion chamber dividing plate 138 of each override type eddy combustion chamber mixing exhaust section 142 end, the override type eddy combustion chamber volute 137 in relief opening 99 outsides, override type eddy combustion chamber is provided with override type eddy combustion chamber exhaust air collecting chamber 144, override type eddy combustion chamber relief opening 99 is communicated with override type eddy combustion chamber exhaust air collecting chamber 144, override type eddy combustion chamber exhaust air collecting chamber 144 joins with the exhaust passage, override type eddy combustion chamber 98 of annular and is communicated with, and is respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 on override type eddy combustion chamber gas-entered passageway 166 and the exhaust passage, override type eddy combustion chamber 98.Other is identical with embodiment one, two or three.

The eddy combustion chamber is a kind of distortion of turbocharger; Eddy combustion chamber dividing plate is divided into multistage (Fig. 1 with the eddy combustion chamber, Fig. 2, Fig. 6 and the two-part eddy combustion chamber that is shown in Figure 7), every section eddy combustion chamber all is a relatively independent firing chamber, every section indoor 3/5ths sections the preceding of eddy combustion are eddy combustion chamber mixed combustion section (being provided with fuel nozzle and igniter), 2/5ths of remainder is eddy combustion chamber mixing exhaust section (being provided with water spout and relief opening), each section eddy combustion chamber forms a collar vortex through dividing plate air passing hole end-to-end, helps the formation in igniting mixed combustion of each section eddy combustion chamber and vortex flow field; The place that override type eddy combustion chamber is different from grade separation type eddy combustion chamber is that gas-entered passageway is not crossed in the exhaust passage, and intake and exhaust channel is non-intersect.Eddy combustion chamber dividing plate is flat, also can adopt taper or circular arc; Being arranged on the collar vortex cross section of eddy combustion chamber, also can be other angle cross section.Suitably strengthen the eddy combustion chamber size, the two-stage at least of connecting behind the eddy combustion chamber is equipped with the turbocharger of solid-liquid body segregating unit, and the eddy combustion chamber can use other gas, solid, liquid or two-phase wherein or the three-phase fluid-mixing fuel that comprises coal dust.When being equipped with turbocharger before the eddy combustion chamber, its gas-entered passageway can adopt a variant wedge-like body regulating controller 3.

Embodiment one and five to nine described eddy combustion chambers, turbocharger, vortex venting gas appliance air inlet section all are the constant speed volutes, described constant speed volute is that a radius is linear change with angle of swing, formed constant speed helix rotates a circle, eddy combustion chamber, turbocharger, vortex venting gas appliance air inlet section are exactly to be the annular volute in cross section with this constant speed helix, its fundamental form line is an involute, and the variable quantity of its radius that rotates a circle is the width of eddy combustion chamber, turbocharger and vortex venting gas appliance suction port; The fluid characteristics of constant speed volute is, the no angle of attack incident of medium, and promptly the vector of incident medium stream is identical with constant speed volute inside vortex flow vector, the streamline coincidence.

Embodiment ten: in conjunction with Fig. 4, Fig. 5, Figure 11 to Figure 13, Figure 16 and Figure 17 illustrate present embodiment, the firing chamber of present embodiment is ring rotation firing chamber 71, and ring rotation firing chamber 71 is by ring rotation combustion chamber flame drum 164, ring 86 in the ring rotation firing chamber, ring rotation firing chamber outer shroud 42, fagging 87 before the ring rotation combustion chamber flame drum, ring rotation combustion chamber flame drum rear stay plate 88, compressorshaft gas compressor end core barrel 52, compressorshaft ratchet end core barrel 21, ring rotation firing chamber gas-entered passageway 167, ring rotation exhaust combustion chamber passage 168, at least one the 3rd fuel nozzle 148, at least one is firearm 149 and at least one the 3rd water spout 150 composition thirdly;

Ring

86 and 42 of ring rotation firing chamber outer shrouds are provided with ring rotation combustion chamber flame drum 164 in the ring rotation firing chamber, ring rotation combustion chamber flame drum 164 is made up of ring 43 and ring rotation combustion chamber flame drum outer shroud 40 in the ring rotation combustion chamber flame drum, the preceding fagging 87 of the front end of the front end of ring 86 and ring rotation combustion chamber flame drum 164 and ring rotation combustion chamber flame drum is affixed in the ring rotation firing chamber, the rear end and the ring rotation combustion chamber flame drum rear stay plate 88 of the rear end of ring 86 and ring rotation combustion chamber flame drum 164 are affixed in the ring rotation firing chamber, and fagging 87 and ring rotation combustion chamber flame drum rear stay plate 88 are packed in respectively on the compressorshaft 58 of gas compressor 1 before the ring rotation combustion chamber flame drum; Ring 43, ring rotation combustion chamber flame drum outer shroud 40, the preceding fagging 87 of ring rotation combustion chamber flame drum and ring rotation combustion chamber flame drum rear stay plate 88 are lamination interlayer small structure in the ring rotation combustion chamber flame drum; Ring rotation combustion chamber flame drum 164 is divided into five sections vertically, 3/5ths sections of the ring rotation combustion chamber flame drum 164 of close gas compressor 1 rear end are ring rotation firing chamber mixed

combustion section

151,2/5ths sections of the ring rotation combustion chamber flame drum 164 of close high pressure turbine 7 front ends are ring rotation firing chamber mixing exhaust section 152, be provided with thirdly firearm 149 of at least one the 3rd fuel nozzle 148 and at least one in the ring rotation firing chamber mixed combustion section 151, be provided with at least one the 3rd water spout 150 in the ring rotation firing chamber mixing exhaust section 152, compressorshaft gas compressor end core barrel 52 is conveyance conduits of ring rotation firing chamber fuel, compressorshaft ratchet end core barrel 21 is conveyance conduits of ring rotation high combustion chamber pressures clean water, compressorshaft gas compressor end core barrel 52 joins with at least one the 3rd fuel nozzle 148 and is communicated with, and compressorshaft ratchet end core barrel 21 joins with at least one the 3rd water spout 150 and is communicated with; Ring rotation firing chamber gas-entered passageway 167 is arranged on the outside of ring rotation firing chamber outer shroud 42 and adjacent with gas compressor 1 for annular, ring rotation exhaust combustion chamber passage 168 is respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 for annular is arranged on the outside of ring rotation combustion chamber flame drum outer shroud 40 and adjacent with high pressure turbine 7 on ring rotation firing chamber gas-entered passageway 167 and the ring rotation exhaust combustion chamber passage 168.Other is identical with embodiment one, two or three.

Fagging 87 and ring rotation combustion chamber flame drum rear stay plate 88 are lamination interlayer small structure before the ring rotation combustion chamber flame drum 164 of present embodiment, ring rotation combustion chamber flame drum, interlayer aperture 113 longitudinal cross-sections during according to rated power in burner inner liner linear velocity and the burner inner liner each section design airspeed and rate-of flow determine; It is slightly larger near the lamination interlayer small aperture of relief opening on the high pressure turbine side ring shape revolving combustor burner inner liner outer shroud 40 to be positioned at ring rotation firing chamber mixing exhaust section 152, percent opening is higher, so that be connected mutually with the exhaust passage, its lamination 112 interlayer directions are opposite with flame tube wall import lamination interlayer direction, and lamination interlayer direction is in face of gas comes flow path direction.

Embodiment 11: in conjunction with Fig. 3, Fig. 8, Figure 11 to Figure 13 and Figure 16 and Figure 17 illustrate present embodiment, the firing chamber of present embodiment is a tubular revolving combustor 54, and tubular revolving combustor 54 is by front end axle 165, rear end axle 67, tubular revolving combustor frame 89, tubular revolving combustor burner inner liner 41, tubular revolving combustor front end axle center pipe 155, axle center, tubular revolving combustor rear end pipe 75, tubular revolving combustor gas-entered passageway 169, tubular revolving combustor exhaust passage 170, two end axle faggings 84, two burner inner liner indent end plates 85, a plurality of hollow stator blades 81, at least one the 4th fuel nozzle 156, at least one the 4th igniter 157 and at least one the 4th water spout 158 are formed; Be provided with tubular revolving combustor burner inner liner 41 in the chamber of tubular revolving combustor frame 89, the front-end and back-end of tubular revolving combustor burner inner liner 41 respectively are provided with a burner inner liner indent end plate 85, two burner inner liner indent end plates 85 are affixed with front end axle 165 and rear end axle 67 respectively at the two ends of tubular revolving combustor burner inner liner 41, front end axle 165 and rear end axle 67 respectively are provided with an end axle fagging 84 perpendicular to two burner inner liner indent end plate 85 end faces, two end axle faggings 84 respectively with front end axle 165, rear end axle 67 and two burner inner liner indent end plates 85 are affixed, front end axle 165 is an axon with the compressorshaft 58 of gas compressor 1, rear end axle 67 is by the end transmission joint of ratchet type overrunning clutch 57 with the high pressure turbine axle 6 of high pressure turbine 7, front end axle 165 and compressorshaft 58 are provided with tubular revolving combustor front end axle center pipe 155, tubular revolving combustor front end axle center pipe 155 joins with at least one the 4th fuel nozzle 156 and is communicated with, rear end axle 67 is provided with axle center, tubular revolving combustor rear end pipe 75, and axle center, tubular revolving combustor rear end pipe 75 joins with at least one the 4th water spout 158 and is communicated with; Tubular revolving combustor burner inner liner 41, two end axle faggings 84 and two burner inner liner indent end plates 85 are lamination interlayer small structure; Tubular revolving combustor burner inner liner 41 evenly is divided into five sections vertically, 3/5ths sections of the tubular revolving combustor burner inner liner 41 of close gas compressor 1 rear end are tubular revolving combustor

mixed combustion section

153,2/5ths sections of the tubular revolving combustor burner inner liner 41 of close high pressure turbine 7 front ends are tubular revolving combustor mixing exhaust section 154, be provided with at least one the 4th fuel nozzle 156 and at least one the 4th igniter 157 in the tubular revolving combustor mixed combustion section 153, be provided with at least one the 4th water spout 158 in the tubular revolving combustor mixing exhaust section 154; Tubular revolving combustor gas-entered passageway 169 is arranged on the outside of tubular revolving combustor frame 89 and adjacent with gas compressor 1, and tubular revolving combustor exhaust passage 170 is arranged on the outside of tubular revolving combustor burner inner liner 41 and adjacent with high pressure turbine 7; Intersect a plurality of hollow stator blades 81 that are provided with equidistant arrangement on the section at annular space between tubular revolving combustor burner inner liner 41 and the tubular revolving combustor frame 89 and tubular revolving combustor exhaust passage 170, being tubular revolving combustor exhaust passage 170 in each hollow stator blade 81, is compressed air channel outside each hollow stator blade 81; Be respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 on tubular revolving combustor gas-entered passageway 169 and the tubular revolving combustor exhaust passage 170.Other is identical with embodiment one, two or three.

The tubular revolving combustor burner inner liner 41 of present embodiment can be an Any shape tubular solid of rotation; The utility model preferably adopts similar apple shape, like recess in base of fruit and the bud two ends is burner inner liner indent end plate 85, front end axle 165 and rear end axle 67 respectively are provided with an end axle fagging 84 perpendicular to burner inner liner indent end plate 85 end faces, constitute the three-dimensional three-support structure of two ends end axle; Tubular revolving combustor burner inner liner 41, two end axle faggings 84 and two burner inner liner indent end plates 85 are lamination interlayer small structure, the longitudinal cross-section of interlayer aperture 113 during according to tubular revolving combustor burner inner liner 41 rated power in linear velocity and the tubular revolving combustor burner inner liner 41 each sections design airspeed and rate-of flow determine; The aperture that is positioned at relief opening lamination interlayer aperture on the high pressure turbine 7 side flame tube walls of tubular revolving combustor mixing exhaust section 154 is slightly larger, percent opening is higher, so that be connected mutually with the exhaust passage, its lamination 112 interlayer directions are opposite with the lamination interlayer direction of tubular revolving combustor flame tube wall airflow inlet, and lamination interlayer direction is in face of gas comes flow path direction.

The described turbocharger of above-mentioned embodiment, the vortex venting gas appliance, in eddy combustion chamber and the revolving combustor and advance, the Rafael nozzle throat that position variant wedge-like body regulating controller 3 that is provided with on the exhaust passage or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted is equipped with temperature, pressure and velocity transducer, be provided with the creep sensor in the firing chamber, relevant duty parameter promptly and accurately feeds back to computer regulating center (not shown), the computer regulating center is according to relevant apparatus real-time parameter and design parameter and operating mode control command, use the high-speed computation of operating mode control program and send instruction in real time, execution and servomechanism (not shown) are according to computer regulating center instruction real-time monitoring firing chamber fuel straying quatity and injection flow rate, movable wedge-like body 30 positions of regulation and control position variant wedge-like body regulating controller 3 or deformable wedge-like body 37 shapes of deformation formula wedge-like body regulating controller 4, the equivalent section of the position of ring 49 and then adjusting vortex venting gas appliance relief opening 48 in the adjustable outer shroud 47 relative vortex venting gas appliance of regulation and control vortex venting gas appliance, make the firing chamber under permanent Continuous Flow prerequisite, realize changeable burning heat absorption and heat exchange of flash evaporation, make turbocharger, dynamic compression is realized in vortex venting gas appliance and eddy combustion chamber under vortex flow field effect effect, stable operation under the design conditions parameter.

What described eddy combustion chamber and revolving combustor adopted is the changeable burning heat absorption of a kind of permanent continuous vortex flow technology; In the eddy combustion chamber, medium prolongs eddy combustion chamber constant speed volute involute shape gas-entered passageway and enters the eddy combustion chamber, the flow velocity of medium increases, can change the kinetic energy of medium in the part of medium earlier into, in the indoor formation vortex of eddy combustion flow field, described vortex flow field overlaps (fluid characteristics of constant speed volute) with the MEDIA FLOW streamline of incident, incident medium flows to the vortex flow momentum, vortex flow gives the incident MEDIA FLOW negative pressure-induced, and both further improve the velocity of medium of mutually promoting, under the vortex effect effect, the stack of MEDIA FLOW streamline convolution potential barrier, at the vortex flow center, the vortex flow flow velocity descends, and described kinetic energy further changes the potential energy of medium into; The revolving combustor burner inner liner is with high pressure turbine 7 and gas compressor 1 high speed rotating, revolving combustor flame tube wall lamination interlayer small structure with certain moment of momentum produces the pumping over and the check effect of moving blades, pumping over and to induce the relatively low air of pressure to enter rotary combustion indoor; Described eddy combustion chamber and revolving combustor are in the scalar field vector field characteristic of fluid and the velocity field of vortex flow, pressure field, the temperature field, under energy field effect and the effect of potential barrier synergistic effect, advance in eddy combustion chamber and revolving combustor, under the Rafael nozzle critical effect effect that the throat section that position variant wedge-like body regulating controller of installing on the exhaust passage 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted is adjustable, in fuel-air mixed combustion process, produce changeable effect, when medium temperature raises, the pressure of medium gets a promotion synchronously, realize that thermomechanics is referred to as changeable change of state, the pressure that makes medium is realized the permanent continuous-flow of medium simultaneously comparatively near the pressure ratio of average endothermic temperature correspondence.

Mixing exhaust section at described eddy combustion chamber and revolving combustor, under the changeable state of same permanent continuous vortex flow, allow and directly contact with the high-temperature fuel gas air mixture through an amount of high-pressure atomization clean water of preheating, atomizing clean water pressure descends suddenly, make the clean water atomizing trickleer, simultaneous temperature raises suddenly, rapid flash vaporization mixed heat transfer, and the gas-air water vapor mixture of generation tends to same temperature; This is that a kind of nothing defines the heat exchange that heat transfer surface does not have the temperature difference, and heat transfer surface is exactly tiny atomizing clean water drop surface; The gas-air water vapor mixture temperature that produces descends significantly, and the pressure of medium gets a promotion, and makes the further approaching on average pressure ratio of endothermic temperature correspondence of pressure of medium; Reduced the use amount of oozing the cold compression air, can adopt lower excess air coefficient, atomize simultaneously clean water also can in and combustion gas in the part harmful gas.

Conventional heat exchange since fixedly heat transfer surface exist and be confined to conduct heat exchange between heat exchange medium, heat transfer surface both sides heat exchange medium must have fixed difference difference existence simultaneously; The heat exchange method that the present invention releases does not have the heat transfer surface of defining, and heat transfer surface is exactly tiny atomizing clean water drop surface, be a kind ofly collect that conduction, convection current, the width of cloth are penetrated, comprehensive heat exchange that multiphase flow, evaporation, mixing combine together, the heat exchange medium temperature difference goes to zero; Thereby its exchange rate and efficient are that conventional (existing or known) heat exchange method and heat-exchange apparatus are incomparable.Be stressed that " in right amount " two words in " allow and directly contact with the high-temperature fuel gas air mixture " through an amount of high-pressure atomization clean water of preheating, be a key that keeps firing chamber and even whole unit thermodynamic equilibrium, advanced numeral and control technique make it become possibility.

At turbocharger, in eddy combustion chamber and the vortex venting gas appliance, medium is when prolonging involute shape gas-entered passageway constant speed volute and enter described device, follow principle of conservation of momentum, the flow velocity of medium increases, at turbocharger, form stable vortex flow field in eddy combustion chamber and the vortex venting gas appliance, described vortex flow field overlaps (fluid characteristics of constant speed volute) with the identical streamline of MEDIA FLOW vector of incident, incident medium flows to the vortex flow momentum, vortex flow give the incident MEDIA FLOW be lower than static pressure first dynamic head value is negative pressure-induced mutually promotes, velocity of medium further improves (velocity of medium raising, energy source is in the interior energy of medium), can change the kinetic energy of medium in the part of medium into, the temperature of the horizontal medium of energy descends to some extent in characterizing; At turbocharger, in eddy combustion chamber and the vortex venting gas appliance, medium is in the velocity field of vortex flow, pressure field, the temperature field, under energy field effect and the effect of potential barrier synergistic effect, advance simultaneously in the scalar field of fluid and vector field characteristic and described device, under the Rafael nozzle critical effect effect that the throat section that position variant wedge-like body regulating controller of installing on the exhaust passage 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted is adjustable, the stack of vortex flow streamline convolution potential barrier, at turbocharger, eddy combustion chamber and vortex venting gas appliance collar vortex vortex flow center are like the solid Rotary District, the vortex flow flow velocity descends, medium is dynamically compressed, described kinetic energy further changes the potential energy of medium into, pressure medium gets a promotion, the stack of the said apparatus effect of series connection, make the pressure of medium exceed the pressure ratio of average endothermic temperature correspondence, realize the permanent continuous-flow of medium simultaneously.

Described medium and fluid mean the thermomechanics that comprises the air fuel gas water vapor and the state of aggregation material with particular community on fluid mechanics and the dynamic significance; The collar vortex of occurring in nature and vortex flow be not owing to there is fixing border, the system and the external world unavoidably exist momentum and energy interchange, vortex is constantly produced and extinction, turbocharger of the present invention, eddy combustion chamber and vortex venting gas appliance have the fixedly collar vortex vortex flow system boundary of a constant speed volute, though because unavoidably there is the lower boundary layer of flow velocity in the stickiness of being stained with of fluid near solid face, than the collar vortex of occurring in nature and vortex flow more near perfect condition; Because the scalar field and the vector field characteristic of fluid, the vortex flow field is that a high voltage control district is again a low pressure source; Vortex flow is the hot machine of occurring in nature, but it also not exclusively follows the present mankind's thermodynamics and kinetics and hot machine Cyclical Theory.

Below in conjunction with preferred embodiment, accompanying drawing is described further.

Preferred embodiment 1: for adopting the vortex combustion and steam turbine of grade separation type eddy combustion chamber 93, in conjunction with Fig. 1, Fig. 5, Fig. 6, Fig. 9 to Figure 15 illustrates present embodiment, and the vortex combustion and steam turbine of present embodiment is by Starter 55, Starter clutch 56, gas compressor 1, the multistage grade separation type turbocharger of four groups of series connection, grade separation type eddy combustion chamber 93, ratchet type overrunning clutch 57, high pressure turbine 7, cover shaft type differential coupling 10, intermediate pressure turbine 8, low pressure turbine 14, position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4, vortex venting gas appliance 53, computer regulating center (not shown), carry out and servomechanism (not shown) and other subsidiary body's (not shown) composition; Starter 55 adopts motor, also can adopt internal-combustion engine or pneumatic machinery, need establish gas storage equipment when adopting pneumatic machinery, the Starter output shaft 65 of Starter 55 is in transmission connection by the end of Starter clutch 56 with the compressorshaft 58 of gas compressor 1, and an end of the high pressure turbine axle 6 of high pressure turbine 7 is in transmission connection by the other end of ratchet type overrunning clutch 57 with compressorshaft 58; The cover shaft type low pressure turbine axle 13 of the intermediate pressure turbine axle 9 of intermediate pressure turbine 8 and low pressure turbine 14 is affixed with two taper driving gears 24 of cover shaft type differential coupling 10 respectively, power is by stub 16 outputs of cover shaft type differential coupling 10, the connection of joining of the annular inlet passageway of the first order grade separation type turbocharger of the multistage grade separation type turbocharger that the annular waste air duct of gas compressor 1 is connected with first group, the annular waste air duct of the final stage grade separation type turbocharger of the multistage grade separation type turbocharger of first group of series connection is joined with the annular inlet passageway of grade separation type eddy combustion chamber 93 and is communicated with, the connection of joining of the annular inlet passageway of the first order grade separation type turbocharger in the multistage grade separation type turbocharger that the annular waste air duct of grade separation type eddy combustion chamber 93 is connected with second group, the annular waste air duct of the final stage grade separation type turbocharger of the multistage grade separation type turbocharger of second group of series connection is joined with the annular inlet passageway of high pressure turbine 7 and is communicated with, the connection of joining of first order grade separation type turbocharger annular inlet passageway in the multistage grade separation type turbocharger that the annular waste air duct of high pressure turbine 7 is connected with the 3rd group, the final stage grade separation type turbocharger annular waste air duct of the multistage grade separation type turbocharger of the 3rd group of series connection is joined with the annular inlet passageway of intermediate pressure turbine 8 and is communicated with, the connection of joining of first order grade separation type turbocharger annular inlet passageway in the multistage grade separation type turbocharger that the annular waste air duct of intermediate pressure turbine 8 is connected with the 4th group, the final stage grade separation type turbocharger annular waste air duct of the multistage grade separation type turbocharger of the 4th group of series connection is joined with the annular inlet passageway of low pressure turbine 14 and is communicated with, the annular waste air duct of low pressure turbine 14 is joined with the annular inlet passageway of vortex venting gas appliance 53 and is communicated with, the array-type relief opening of vortex venting gas appliance 53 is communicated with atmosphere, and wherein the annular waste air duct of upper level grade separation type turbocharger is joined with the annular inlet passageway of its next stage grade separation type turbocharger and is communicated with in the multistage grade separation type turbocharger of four groups of series connection; In grade separation type eddy combustion chamber mixed combustion section 90, the heat absorption of under changeable state, burning of air and fuel; In grade separation type eddy combustion chamber mixing exhaust section 91, high-temperature fuel gas air mixture and the surperficial flash vaporization mixed heat transfer that directly contacts of an amount of high-pressure atomization clean water fine drop; In grade separation type turbocharger 2, grade separation type eddy combustion chamber 93 and vortex venting gas appliance 53, with the interior dynamic compression that can realize medium of medium; Advancing of grade separation type turbocharger 2 and grade separation type eddy combustion chamber 93, be respectively arranged with a position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 on the exhaust passage and (also can adopt the adjustable variable stator vane angle of the angle of attack, flow resistance was bigger when its shortcoming was low discharge), position variant wedge-like body regulating controller 3 that is provided with on the exhaust passage of grade separation type turbocharger 2 in the series connection and grade separation type eddy combustion chamber 93 or deformation formula wedge-like body regulating controller 4, position variant wedge-like body regulating controller 3 on double as next stage grade separation type turbocharger or grade separation type eddy combustion chamber 93 gas-entered passageways or deformation formula wedge-like body regulating controller 4; First order turbocharger and vortex venting gas appliance 53 in the multistage turbocharger of four groups of series connection are respectively arranged with a solid-liquid body segregating unit.

During startup, Starter 55 drives gas compressor 1 running by Starter clutch 56, owing to be provided with ratchet type overrunning clutch 57 between high pressure turbine axle 6 and the compressorshaft 58, high pressure turbine 7 is not along with rotation.Described ratchet type overrunning clutch 57 is interior engagement, many ratchets (number n of ratchet 〉=2) all-meshing type ratchet unit, and promptly ratchet is the integral multiple of ratchet, the ratchet spaced set.When the medium in the high pressure turbine 7 previous stage grade separation type turbochargers 2 has certain pressure, high pressure turbine 7 starts automatically, when high pressure turbine axle 6 revolutions are higher than compressorshaft 58 revolutions, high pressure turbine axle 6 drives compressorshaft 58 accelerated services through ratchet type overrunning clutch 57, this design can reduce the Starter design power and quicken start-up course, and the full mesh ratchet gear formula of many ratchets free wheel device can satisfy the transmission of high speed high pulling torque simultaneously; When the power of high pressure turbine 7 generations reaches the rated power of gas compressor 1, computer regulating center (not shown) sends instruction in real time, with actuator (not shown) regulation and control Starter clutch 56 it is separated by servo, vortex combustion and steam turbine finishes starting state, enters the normal operation pattern.The pressurized air that gas compressor 1 comes out on the first order grade separation type turbocharger gas-entered passageway of multistage grade separation type turbocharger of first group of series connection position variant wedge-like body regulating controller 3 or the Rafael nozzle of deformation formula wedge-like body regulating controller 4 structure shape lines formation accelerate to threshold state, and maintenance maximum volume flow, grade separation type turbocharger gas-entered passageway 159 via constant speed volute involute shape is entered in the first order grade separation type turbocharger of first group of multistage grade separation type turbocharger of connecting by grade separation type turbocharger suction port 45, form stable vortex flow field within it, vortex flow streamline vector in the first order grade separation type turbocharger of multistage grade separation type turbocharger of incident air-flow and first group of series connection is identical, streamline overlaps (fluid characteristics of constant speed volute), the incident air-flow is given the vortex flow momentum, vortex flow is quickened, vortex flow feeds the stream of emanating and is lower than first dynamic head value back pressure of static pressure, negative pressure-induced mutually promoting, the Rafael nozzle extending section that incident air-flow variant wedge-like body on the throne regulating controller 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted further quickens to be supersonic airstream; The incident air-flow enters in the first order grade separation type turbocharger of first group of multistage grade separation type turbocharger of connecting along the grade separation type turbocharger gas-entered passageway 159 of involute constant speed volute annular, because momentum conservation, flow velocity further improves, velocity of medium improves, energy source is in the interior energy of medium, can change the kinetic energy of medium in the part of medium into, the temperature of the horizontal medium of energy descends to some extent in characterizing; Potential barrier stack in the first order grade separation type turbocharger of first group of multistage grade separation type turbocharger of connecting, the streamline convolution, in described turbocharger annular center like the solid Rotary District, the vortex flow flow velocity descends, reduce to zero at center of vorticity place flow velocity, under velocity field, pressure field, temperature field, energy field effect and the effect of potential barrier synergistic effect of vortex flow, the high speed vortex flow is dynamically compressed, the part kinetic energy of fluid changes the potential energy (potential energy) of fluid into, the stagnation voltage rise height of medium; Because the macroscopic motion fluid not only has the scalar field characteristic, has the vector field characteristic simultaneously, the back pressure that acts on the incident air-flow is then for being lower than first dynamic head value of static pressure; Because the vortex flow field exists, the vortex flow streamline vector interior owing to incident air-flow and turbocharger is identical, streamline overlaps, because the critical effect of the Rafael nozzle that position variant wedge-like body regulating controller of installing on the described turbocharger inlet and outlet passage 3 or deformation formula wedge-like body regulating controller 4 structure shape throat sections that line constitutes are adjustable raises described turbocharger fluid pressure; The position variant wedge-like body regulating controller of installing on grade separation type turbocharger 2 gas-entered passageways 3 or the threshold state of deformation formula wedge-like body regulating controller 4 have been blocked the upstream propagation of described turbocharger internal pressure disturbance, the Rafael nozzle threshold state that position variant wedge-like body regulating controller of installing on the described turbocharger exhaust passage 3 or deformation formula wedge-like body regulating controller 4 structure shape throat sections that line constitutes are adjustable is just as a stifled adjustable height barrage, make pressure medium rising in the turbocharger, realize the permanent continuous-flow of medium simultaneously; In the first order grade separation type turbocharger of multistage grade separation type turbocharger of first group of series connection, solid-liquid body suspended matter is separated by the first solid-liquid body segregating unit 121 and collects in the medium; Medium with certain pressure and temperature, position variant wedge-like body regulating controller of installing on the first order grade separation type turbocharger exhaust passage of multistage grade separation type turbocharger of first group of series connection 3 or deformation formula wedge-like body regulating controller 4 enter in the second level grade separation type turbocharger of multistage grade separation type turbocharger of first group of series connection according to the sample potential barrier dynamic compression that superposes, enter the third level grade separation type turbocharger and the later grade separation type turbocharger dynamic compression at different levels of the multistage grade separation type turbocharger of first group of series connection subsequently successively, the final stage grade separation type turbocharger of multistage grade separation type turbocharger of first group of series connection comes out has uniform temperature and pressure medium, enter grade separation type eddy combustion chamber gas-entered passageway 136 through its exhaust passage, be accelerated in position variant wedge-like body regulating controller of on described air-flow path, installing 3 or the deformation formula wedge-like body regulating controller 4, the Rafael nozzle throat that is constituted at its structure shape line reaches threshold state, quickens to become supersonic airstream in extending section dilatation subsequently; High velocity air enters grade separation type eddy combustion chamber 93 along the grade separation type eddy combustion chamber gas-entered passageway 136 of constant speed volute involute annular, because momentum conservation, air-flow further is accelerated, can change the kinetic energy of medium in the part of medium earlier into, in the stable vortex flow field of the indoor formation of described eddy combustion, this vortex flow field overlaps with the MEDIA FLOW streamline of incident, (light by first igniter 134 during startup in grade separation type eddy combustion chamber mixed combustion section 90 and the fuel mix burning that sprays into by first fuel nozzle 133, starting the back is lighted by the temperature more than the steady combustion district burning-point, described steady combustion district is the lower seemingly solid Rotary District of eddy combustion chamber central medium flow velocity), under the vortex effect effect, advance at this device, under the Rafael nozzle critical effect effect that the throat section that position variant wedge-like body regulating controller of installing on the exhaust passage 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted is adjustable, the stack of MEDIA FLOW streamline convolution potential barrier, at collar vortex vortex flow center, eddy combustion chamber, the vortex flow flow velocity descends, in fuel-air mixed combustion process, produce changeable effect, the temperature of medium raises, pressure rises to synchronously, can change the potential energy of medium in the kinetic energy of medium and the part into.Along with burning is carried out, gas-air mixture is rotating to mixing exhaust section 91 precession of grade separation type eddy combustion chamber with certain speed and is advancing; In this mixing exhaust section, the high-temperature fuel gas air mixture directly contacts with the clean water through preheating, supercharging (an amount of) the fine drop surface that is sprayed into by 135 atomizings of first water spout, atomized water pressure descends suddenly, make the clean water atomizing trickleer, simultaneous temperature raises suddenly, rapidly the flash vaporization mixed heat transfer; Do not define heat transfer surface, the heat transfer surface clean water fine drop surface that atomizes exactly, the gas-air water vapor tends to same temperature, its heat exchange efficiency and thermal conduction rate be other any heat exchange mode and heat transmission equipment can't than like, save huge poor efficiency heat transmission equipments such as the hot machine boiler of conventional steam turbine and combined type.Because the vortex flow field exists, this process is confined to center, eddy combustion chamber near zone, and the survival that avoids evaporating accumulates on the volute of eddy combustion chamber; Because the thermal capacity of water vapor is bigger, merge combustion gas, air and water vapor mixture that evaporation produces, descend significantly than the gas-air mixture temperature, because the threshold state of the adjustable Rafael nozzle in throat section that position variant wedge-like body regulating controller 3 that the vortex flow field exists and described eddy combustion chamber inlet and outlet passage is installed or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted and vortex flow field exist, pressure then raises to some extent; Medium temperature descends, reduced the use amount of oozing the cold compression air, can adopt lower excess air coefficient, alleviate the load of gas compressor 1, the content of NOx in the weary gas of corresponding minimizing, the parts that contact with medium can adopt conventional heat-resistant material to manufacture, and effectively reduce this device fabrication cost, improve the reliability of this equipment operation; The clean water that atomizes simultaneously can neutralize part harmful gas in the combustion gas, effectively alleviates the pollution to environment; Described first water spout, 135 atomized sprays are opened and are ended valve employing high back pressure spring, and the clean water High Pressure Difference is sprayed in the grade separation type eddy combustion chamber mixing exhaust section 91.Because the fluid characteristics of constant speed volute and fluid vectors field, because the existence in vortex flow field, the gas-air water vapor mixture of the indoor elevated pressures of eddy combustion can not gone up north adverse current; Simultaneously because north check effect on volume flow maintenance and the pressure wave under the adjustable Rafael nozzle threshold state in throat section that position variant wedge-like body regulating controller of installing on the inlet and outlet passage of eddy combustion chamber 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted, make grade separation type eddy combustion chamber 93 realize changeable (in many ways) burning heat absorption and flash distillation mixed heat transfer, the pressure that makes medium is realized the permanent continuous-flow of medium simultaneously near the corresponding pressure ratio of average endothermic temperature.

The middle temperature gas-air water vapor mixture of certain pressure is come out to have in grade separation type eddy combustion chamber 93, at first enter the first order grade separation type turbocharger dynamic compression of the multistage grade separation type turbocharger of second group of series connection, the multistage grade separation type turbocharger second level that enters second group of series connection subsequently successively reaches grade separation type turbocharger dynamic compression at different levels later on, the flue dust that fuel combustion produces in the medium is separated by the first solid-liquid body segregating unit of installing on the one-level grade separation type turbocharger in the multistage grade separation type turbocharger of second group of series connection 121 and collects, the final stage grade separation type turbocharger of multistage grade separation type turbocharger of the second group of series connection middle temperature of coming out, high-pressure gas air-steam mixture, because the stack of multistage grade separation type turbocharger and grade separation type eddy combustion chamber 93 effects again, its pressure is considerably beyond the corresponding pressure ratio of average endothermic temperature, position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 through being arranged on its exhaust passage enter high pressure turbine 7 expansion workings, the high pressure turbine axle 6 of high pressure turbine 7 drives compressorshaft 58 runnings of gas compressor 1 through ratchet type overrunning clutch 57, the medium that high pressure turbine 7 is discharged enters the multistage grade separation type turbocharger dynamic compression of the 3rd group of series connection successively, pressure medium is restored or the part recovery, simultaneously water of condensation is separated by the solid-liquid body segregating unit installed on the first order grade separation type turbocharger in the multistage grade separation type turbocharger of the 3rd group of series connection and collect, recycle for vortex combustion and steam turbine after treatment; Described then medium enters intermediate pressure turbine 8 expansion workings, intermediate pressure turbine 8 come out medium enter successively the 4th group the series connection multistage grade separation type turbocharger, making pressure medium obtain part recovers, while is separated water of condensation by the solid-liquid body segregating unit of installing on the first order grade separation type turbocharger in the multistage grade separation type turbocharger of the 4th group of series connection and collects, and the treated vortex combustion and steam turbine that supplies recycles; Medium enters low pressure turbine 14 expansion workings then, the weary gas of the low-pressure low-temperature that low pressure turbine 14 comes out enters vortex venting gas appliance 53, weary gas through vortex venting gas appliance gas-entered passageway 126 along constant speed volute involute shape vortex venting gas appliance air inlet section 73 volutes and air guide volute 78 by the vortex venting gas appliance in suction port 51 and vortex venting gas appliance external admission mouth 50 enter vortex venting gas appliance air inlet section 73, because the flow velocity of the weary gas of momentum conservation increases, can change kinetic energy in the part of weary gas, form the vortex flow field of an annular in vortex venting gas appliance air inlet section 73, tangential external vortex venting gas appliance changeover portion 80 in this annular vortex flow field and vortex venting gas appliance exhaust section 163 form an approximate ellipsoidal collar vortex again, two collar vortexs are overlapped, and mutually promote; Weary simultaneously gas is given the vortex flow momentum, vortex flow is lower than first dynamic head value back pressure of static pressure to weary one in the gas of incident, mutually promote, the stack of streamline convolution potential barrier, descending like solid Rotary District flow velocity of vortex flow, vortex flow is dynamically compressed, efficient diffusion, when weary atmospheric pressure during, enter atmosphere through the adjustable relief opening of vortex venting gas appliance a little more than atmospheric pressure; Vortex venting gas appliance air inlet section is provided with the 3rd solid-liquid body segregating unit 141, will lack in the gas water of condensation and other solid-liquid body separating substances and collects, and water of condensation recycles for vortex combustion and steam turbine after treatment; The cover shaft type low pressure turbine axle 13 of the intermediate pressure turbine axle 9 of intermediate pressure turbine 8 and low pressure turbine 14 is connected by cover shaft type differential coupling 10 differentials, cover shaft type differential coupling 10 is by the self adaption differential rotation of its planetary pinion 12, realize that intermediate pressure turbine 8 and low pressure turbine 14 revolution self adaption dynamic differentials are regulated, the enthalpy drop dynamic assignment, effectively reduced the leaving loss of unit; Complete machine power is by stub 16 outputs of cover shaft type differential coupling 10.Described vortex combustion and steam turbine all devices is by the unified control in a computer regulating center; The revolution of Starter and other parameter, gas compressor, high, in, the low pressure turbine revolution, gas compressor, turbochargers at different levels, the firing chamber, high, in, low pressure turbine and vortex venting gas appliance 53 medium pressure, flow velocity and temperature, the Rafael nozzle throat medium temperature that position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted, pressure, flow velocity, Starter clutch 56 states, the creep of firing chamber member, the fuel straying quatity, injection flow rate, and other accessory operating mode, by various kinds of sensors and other parameter acquisition device the relevant device duty parameter is in time fed back to the computer regulating center; The computer regulating center reaches design parameter and staff's real-time command in real time according to each equipment, use the high-speed integrated computing of operating mode control program, send regulation and control instruction in real time, relevant execution and servomechanism instruct according to the computer regulating center, adjust the relevant device control in real time, make the steady running under design conditions of vortex combustion and steam turbine.

Preferred embodiment 2: for adopting the vortex combustion and steam turbine of override type eddy combustion chamber 97, in conjunction with Fig. 2, Fig. 7, Fig. 9-Figure 15 illustrates present embodiment, and the vortex combustion and steam turbine of present embodiment is by Starter 55, Starter clutch 56, gas compressor 1, the multistage override type turbocharger of first group and second group series connection, the multistage grade separation type turbocharger of the 3rd group and the 4th group series connection, override type eddy combustion chamber 97, ratchet type overrunning clutch 57, high pressure turbine 7, cover shaft type differential coupling 10, intermediate pressure turbine 8, low pressure turbine 14, position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4, vortex venting gas appliance 53, computer regulating center (not shown), carry out and servomechanism (not shown) and other fixture (not shown) composition.Preferred embodiment 2 is different from preferred embodiment 1 part and is: preposition turbocharger of this preferred embodiment high pressure turbine and eddy combustion chamber are override type turbocharger 20 and override type eddy combustion chamber 97, grade

separation type turbocharger

2 and 93 differences of grade separation type eddy combustion chamber adopted with preferred embodiment 1 only are, gas-entered passageway is not crossed in the exhaust passage, intake and exhaust channel is non-intersect, gas-entered passageway is fit to adopt deformation formula wedge-like body regulating controller 4 when using separately, be fit to use with the radial-flow type mechanical engagement, it is advantageous that the exchange of intake and exhaust empty calory, when plural serial stage used, axial length was shorter; Its action principle is the same with grade separation type turbocharger 2 and grade separation type eddy combustion chamber 93 that embodiment 1 adopts; Other is all identical with embodiment 1.

Preferred embodiment 3: for adopting the vortex combustion and steam turbine of ring rotation firing chamber 71, in conjunction with Fig. 4, Fig. 5, Fig. 9-Figure 17 illustrates this preferred embodiment, and the vortex combustion and steam turbine of this preferred embodiment is by Starter 55, Starter clutch 56, gas compressor 1, the multistage grade separation type turbocharger of four groups of series connection, ring rotation firing chamber 71, ratchet type overrunning clutch 57, high pressure turbine 7, cover shaft type differential coupling 10, intermediate pressure turbine 8, low pressure turbine 14, position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4, vortex venting gas appliance 53, computer regulating center (not shown), execution and servomechanism and other fixture (not shown) are formed; Comparison diagram 1 and Fig. 4 are not difficult to find, this preferred embodiment is with the difference of preferred embodiment 1: this reality is preferably executed example and is adopted ring rotation firing chamber 71, what preferred embodiment 1 adopted is grade separation type eddy combustion chamber 93, the firing chamber preposition with post equipment, flow process and interrelated all identical with preferred embodiment 1.

The pressurized air that the final stage grade separation type turbocharger of the multistage grade separation type turbocharger of first group of series connection comes out with certain pressure and temperature, enter ring rotation firing chamber gas-entered passageway 167 through grade separation type turbocharger exhaust passage 160, the Rafael nozzle that position variant wedge-like body regulating controller 3 that is provided with in ring rotation firing chamber gas-entered passageway 167 and grade separation type turbocharger exhaust passage 160 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted reaches threshold state, enter annular space between ring rotation firing chamber outer shroud 42 and the ring rotation combustion chamber flame drum outer shroud 40 then, the lamination interlayer aperture on ring rotation combustion chamber flame drum outer shroud 40 enters in the ring rotation combustion chamber flame drum 164; Another strand pressurized air lamination interlayer aperture on the fagging 87 before the ring rotation combustion chamber flame drum enters in the ring rotation combustion chamber flame drum in ring 43 and the ring rotation firing chamber and encircles 86 annular space, enter ring rotation combustion chamber flame drum 164 by the lamination interlayer aperture on the ring 43 in the ring rotation combustion chamber flame drum, the pressurized air that enters burner inner liner with ring rotation combustion chamber flame drum outer shroud 40 converges, produce and burner inner liner sense of rotation 114 rightabout speed, simultaneously because the viscosity effect of medium, on the burner inner liner sense of rotation, produce certain speed, total effect is that the rotational speed of medium is far below the burner inner liner rotational speed; The pressurized air of relatively low pressure is by being entered the relative higher ring rotation combustion chamber flame drum 164 of pressure with the lamination interlayer aperture on the ring rotation flame combustion chamber barrel of gas compressor 1 and high pressure turbine 7 high speed rotating by pumping over.Fuel mixed combustion under changeable state that pressurized air with certain pressure and temperature sprays at ring rotation firing chamber mixed combustion section 151 and the 3rd fuel nozzle 148 (is lighted by firearm 149 thirdly during startup, starting the back is lighted by the above temperature of steady combustion district burning-point, described steady combustion district is the lower annular center zone of ring rotation combustion chamber flame drum velocity of medium), the temperature of medium raises, the pressure of medium gets a promotion synchronously, along with burning is carried out, gas-air mixture is rotating to mixing exhaust section 152 precession of ring rotation firing chamber and is advancing; In ring rotation firing chamber mixing exhaust section 152, high-temperature fuel gas air mixture and the 3rd water spout 150 spray into an amount of directly contacts the rapid flash vaporization of atomized water under changeable state, mixed heat transfer through preheating high-pressure atomization clean water fine drop surface; Described the 3rd water spout 150 atomized sprays are opened and are ended valve employing high back pressure spring.Fuel enters ring rotation combustion chamber flame drum mixed combustion section 151 by compressorshaft gas compressor end core barrel 52, and clean water enters ring rotation firing chamber mixing exhaust section 152 by compressorshaft ratchet end core barrel 21; The gas-air water vapor mixture temperature that produces descends significantly, pressure gets a promotion, because moving blades check and pumping over effect and vortex flow field exist, the gas-air water vapor mixture of elevated pressures adverse current upstream not in the ring rotation combustion chamber flame drum 164, advance owing to the ring rotation firing chamber simultaneously, the critical effect of the adjustable Rafael nozzle in throat section that position variant wedge-like body regulating controller of installing on the exhaust passage 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted, make the ring rotation firing chamber realize changeable burning heat absorption, the flash distillation mixed heat transfer, the pressure that makes medium is near the corresponding pressure ratio of average endothermic temperature.Middle temperature gas-air water vapor mixture with certain pressure, the lamination interlayer aperture of relief opening enters ring rotation exhaust combustion chamber passage 168 on ring rotation combustion chamber flame drum outer shroud, and ring rotation firing chamber 71 obtains certain momentum on the exit flow opposite direction.The middle temperature gas-air water vapor mixture that has certain pressure subsequently enters the multistage grade separation type turbocharger dynamic compression of second group of series connection successively, and is next all identical with preferred embodiment 1.

Preferred embodiment 4: be the vortex combustion and steam turbine that adopts tubular revolving combustor 54, in conjunction with Fig. 3 and Fig. 8-Figure 17 this preferred embodiment is described, the vortex combustion and steam turbine of this preferred embodiment is by Starter 55, Starter clutch 56, gas compressor 1, the multistage grade separation type turbocharger of four groups of series connection, tubular revolving combustor 54, ratchet type overrunning clutch 57, high pressure turbine 7, intermediate pressure turbine 8, low pressure turbine 14, position variant wedge-like body regulating controller 3 or deformation formula wedge-like body regulating controller 4, cover shaft type differential coupling 10, vortex venting gas appliance 53, computer regulating center (not shown), carry out and servomechanism (not shown) and other fixture (not shown) composition.Preferred embodiment 4 is different from preferred embodiment 1 part and is: adopted tubular revolving combustor 54; The compressorshaft 58 and the tubular revolving combustor front end axle 165 of gas compressor 1 are an axon, and tubular revolving combustor rear end axle 67 is in transmission connection by the high pressure turbine axle 6 of ratchet type overrunning clutch 57 with high pressure turbine 7; Preposition and the rearmounted device in firing chamber, flow process and interrelated all identical with preferred embodiment 1.

The air that the final stage grade separation type turbocharger of the multistage grade separation type turbocharger of first group of series connection comes out to have certain pressure and temperature, enter tubular revolving combustor gas-entered passageway 169 through grade separation type turbocharger exhaust passage 160, the adjustable Rafael nozzle medium in throat section that position variant wedge-like body regulating controller 3 that is provided with in tubular revolving combustor gas-entered passageway 169 and grade separation type turbocharger exhaust passage 160 or deformation formula wedge-like body regulating controller 4 structure shape lines constitute is accelerated to threshold state, enter annular space between tubular revolving combustor frame 89 and the tubular revolving combustor burner inner liner 41 then, enter in the tubular revolving combustor burner inner liner 41 by the lamination interlayer aperture on tubular revolving combustor burner inner liner 41 walls, produce and burner inner liner sense of rotation 114 rightabout speed, simultaneously because the viscosity effect of medium, on tubular revolving combustor burner inner liner sense of rotation, produce certain speed, total effect is, the rotational speed of medium is far below the burner inner liner rotational speed, the pressurized air of relatively low pressure or the atmospheric air lamination interlayer aperture on tubular revolving combustor burner inner liner 41 walls is entered the higher relatively tubular revolving combustor burner inner liner 41 of pressure by pumping over, under the effect of moving blades pumping over check effect, media can adverse current in the tubular revolving combustor burner inner liner 41, realizes by low pressure area (the tubular revolving combustor burner inner liner outside of rotation) to the permanent continuous-flow in zone of high pressure (in the tubular revolving combustor burner inner liner).Pressurized air with certain pressure and temperature (is lighted by the 4th igniter 157 during startup in fuel mixed combustion under changeable state that tubular revolving combustor mixed combustion section 153 and the 4th fuel nozzle 156 spray into, starting the back is lighted by the above temperature of steady combustion district burning-point, described steady combustion district is the lower center regions of tubular revolving combustor burner inner liner 41 velocity of medium), the temperature of medium raises, pressure promotes synchronously, along with burning is carried out, gas-air mixture is rotating to 154 precession of tubular revolving combustor mixing exhaust section and is advancing; In tubular revolving combustor mixing exhaust section 154, an amount of directly the contacting that high-temperature fuel gas air mixture and the 4th water spout 158 spray into through preheating high-pressure atomization clean water fine drop surface, the rapid flash vaporization mixed heat transfer of clean water atomizes; Described the 4th water spout 158 atomized sprays are opened and are ended valve employing high back pressure spring.Clean water enters tubular revolving combustor mixing exhaust section 154 by axle center, tubular revolving combustor rear end pipe 75, and fuel enters tubular revolving combustor mixed combustion section 153 through tubular revolving combustor front end axle center pipe 155.Because water vapor thermal capacity is higher, the gas-air water vapor mixture temperature that produces descends significantly, because the vortex flow field exists, advance at the tubular revolving combustor simultaneously, under the Rafael nozzle threshold state that position variant wedge-like body regulating controller of installing on the exhaust passage 3 or deformation formula wedge-like body regulating controller 4 structure shape lines are constituted and the pumping over check effect effect of moving blades, the pressure of medium raises to some extent, make the tubular revolving combustor realize changeable (in many ways) burning heat absorption, mix heat exchange of flash evaporation, the pressure that makes medium is realized the permanent continuous-flow of medium simultaneously near the corresponding pressure ratio of average endothermic temperature.Middle temperature has the gas-air water vapor mixture of certain pressure, the lamination interlayer aperture of relief opening is discharged at a high speed on tubular revolving combustor burner inner liner 41, tubular revolving combustor burner inner liner 41 is obtained and the rightabout moment of momentum of discharge MEDIA FLOW, and the gas-air water vapor mixture enters tubular revolving combustor exhaust passage 170 through hollow stator blade 81 then; Pressurized air is by hollow stator blade 81 outer passage inlet end axle faggings 84 outsides, lamination interlayer aperture on end axle fagging 84 and burner inner liner indent end plate 85 enter tubular revolving combustor mixing exhaust section 154 ooze cold, colling end axle fagging 84 and burner inner liner indent end plate 85 simultaneously.

Tubular revolving combustor burner inner liner 41 comes out to have warm gas-air water vapor mixture in the certain pressure, position variant wedge-like body regulating controller 3 that on its exhaust passage, is provided with or deformation formula wedge-like body regulating controller 4, enter the multistage grade separation type turbocharger dynamic compression of second group of series connection successively, next all identical with preferred embodiment 1.

Claims

1. vortex combustion and steam turbine, described vortex combustion and steam turbine comprise Starter (55), Starter clutch (56), gas compressor (1), firing chamber, ratchet type overrunning clutch (57), cover shaft type differential coupling (10), high pressure turbine (7), intermediate pressure turbine (8) and low pressure turbine (14); It is characterized in that: described vortex combustion and steam turbine also comprises turbocharger, vortex venting gas appliance (53), solid-liquid body segregating unit, wedge-like body regulating controller; Described turbocharger is made up of the 4th group of multistage turbocharger of connecting of setting between the 3rd group of multistage turbocharger of connecting that is arranged on setting between second group of multistage turbocharger of connect being provided with between first group of multistage turbocharger of connecting between gas compressor (1) and firing chamber and firing chamber and high pressure turbine (7), high pressure turbine (7) and intermediate pressure turbine (8), intermediate pressure turbine (8) and low pressure turbine (14); Be respectively arranged with a wedge-like body regulating controller on the inlet and outlet passage of described turbocharger and firing chamber, first order turbocharger and vortex venting gas appliance (53) in the multistage turbocharger of every group of series connection are provided with a solid-liquid body segregating unit; Solid-liquid body segregating unit is respectively the first solid-liquid body segregating unit (121), the second solid-liquid body segregating unit (131) and the 3rd solid-liquid body segregating unit (141), and the first solid-liquid body segregating unit (121), the second solid-liquid body segregating unit (131) are identical with the 3rd solid-liquid body segregating unit (141) structure;

The Starter output shaft (65) of Starter (55) is in transmission connection by the end of Starter clutch (56) with the compressorshaft (58) of gas compressor (1), and an end of the high pressure turbine axle (6) of high pressure turbine (7) is in transmission connection by the other end of ratchet type overrunning clutch (57) with the compressorshaft (58) of gas compressor (1); The intermediate pressure turbine axle (9) of intermediate pressure turbine (8) and the cover shaft type low pressure turbine axle (13) of low pressure turbine (14) are affixed with two taper driving gears (24) of cover shaft type differential coupling (10) respectively, and power is by stub (16) output of cover shaft type differential coupling (10); The connection of joining of the annular waste air duct of gas compressor (1) and the annular inlet passageway of first group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of first group of series connection is joined with the annular inlet passageway of firing chamber and is communicated with, the connection of joining of the annular waste air duct of firing chamber and the annular inlet passageway of second group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of second group of series connection is joined with the annular inlet passageway of high pressure turbine (7) and is communicated with, the connection of joining of the annular waste air duct of high pressure turbine (7) and the annular inlet passageway of the 3rd group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of the 3rd group of series connection is joined with the annular inlet passageway of intermediate pressure turbine (8) and is communicated with, the connection of joining of the annular waste air duct of intermediate pressure turbine (8) and the annular inlet passageway of the 4th group of multistage turbocharger of connecting, the annular waste air duct of the multistage turbocharger of the 4th group of series connection is joined with the annular inlet passageway of low pressure turbine (14) and is communicated with, the annular waste air duct of low pressure turbine (14) is joined with the annular inlet passageway of vortex venting gas appliance (53) and is communicated with, and the relief opening of vortex venting gas appliance (53) is communicated with atmosphere.

2. vortex combustion and steam turbine according to claim 1, it is characterized in that: described wedge-like body regulating controller is a variant wedge-like body regulating controller (3), the position variant wedge-like body regulating controller (3) by position variant wedge-like body regulating controller runner (31), two connecting rods (33), a plurality of movable wedge-like body (30), at least two group position variant wedge-like body regulating controller slideways (32), at least two rooted tooth wheel shafts (19), at least four gears (39) and at least four toothed rack (34), the composition; Gear (39) is identical with both quantity of tooth bar (34), adjacent two toothed rack (34) be arranged in parallel, be packed in respectively on corresponding two connecting rods (33), every rooted tooth wheel shaft (19) is gone up corresponding two gears (39) that install, every toothed rack (34) and an adjacent gear (39) engagement, gear shaft (19) and gear (39) are rotatable components, be fixed with a plurality of movable wedge-like bodys (30) between two connecting rods (33), a plurality of movable wedge-like bodys (30) spaced set, adjacent two movable wedge-like bodys (30) are for be arrangeding in parallel, the movable wedge-like body (30) of corresponding position variant wedge-like body regulating controller slideway (32) is provided with chute, be slidingly matched with at least two group position variant wedge-like body regulating controller slideways (32) by chute connecting rod (33) and a plurality of movable wedge-like body (30), movable wedge-like body (30) has a continuous points of tangency and corresponding with position variant wedge-like body regulating controller runner (31); Every group of position variant wedge-like body regulating controller slideway (32) is two, installs respectively on the corresponding two parallel walls of variant wedge-like body regulating controller runner on the throne (31), and two adjacent groups position variant wedge-like body regulating controller slideway (32) be arranged in parallel.

3. vortex combustion and steam turbine according to claim 1, it is characterized in that: described wedge-like body regulating controller is a deformation formula wedge-like body regulating controller (4), deformation formula wedge-like body regulating controller (4) by deformation formula wedge-like body regulating controller runner (110), a plurality of roller (36), a plurality of deformable wedge-like body (37), organize deformation formula wedge-like body regulating controller slideway (77), a plurality of adjusting axle (38) and a plurality of regulating wheel (35) more and form; Many group deformation formula wedge-like body regulating controller slideways (77) are installed on the corresponding two parallel walls of deformation formula wedge-like body regulating controller runner (110), and two adjacent groups deformation formula wedge-like body regulating controller slideway (77) be arranged in parallel; Each deformable wedge-like body (37) is made up of two spring steel plates, the two ends Joint of two spring steel plates, one end of each deformable wedge-like body (37) is packed on the two corresponding walls of deformation formula wedge-like body regulating controller runner (110), and the other end of each deformable wedge-like body (37) is installed in corresponding deformation formula wedge-like body regulating controller slideway (77) and goes up also and can slide along its orientation; Regulating wheel (35) is oval wheel shape member, the two ends of each regulating wheel (35) are equipped with roller (36), regulating wheel (35) is packed on the adjusting axle (38) and is positioned between two spring steel plates of each deformable wedge-like body (37), and adjusting axle (38) is a rotatable components; Deformation formula wedge-like body regulating controller runner (110) is annular air-flow path, rectangle air-flow path or the comb air-flow path that is provided with the blade-shaped pipe, a plurality of deformable wedge-like bodys (37) are set in qually spaced on annular air-flow path or the rectangle air-flow path, perhaps are separately positioned between the comb of the blade-shaped pipe on the blade-shaped pipe comb air-flow path.

4. vortex combustion and steam turbine according to claim 1 is characterized in that: cover shaft type differential coupling (10) is made up of cross axle (11), stub (16), cross axle scaffold (23), differential coupling housing (5), four planetary pinions (12), two taper driving gears (24), four bearings (60) and two automatic anti-reverse-rotation devices of differential coupling; Four planetary pinions (12) are rotatable to be installed in respectively on the cross axle (11), it is affixed with the middle part of cross axle (11) that one end of stub (16) passes cover shaft type low pressure turbine axle (13), cross axle (11) is packed on the cross axle scaffold (23), cross axle scaffold (23) is installed in respectively on intermediate pressure turbine axle (9) and the cover shaft type low pressure turbine axle (13) by two bearings (60) are rotatable, intermediate pressure turbine axle (9) and cover shaft type low pressure turbine axle (13) are packed in respectively on the corresponding taper driving gear (24), and two taper driving gears (24) are meshed with four planetary pinions (12) respectively; The automatic anti-reverse-rotation device of differential coupling is made up of wheel disc (105), support (104), two axle keys (106), a plurality of wedge shape raceway (107), a plurality of spring (102) and a plurality of ball (103); One end of intermediate pressure turbine axle (9) and cover shaft type low pressure turbine axle (13) is contained in respectively in the central shaft hole of the center hole of support (104) and wheel disc (105), and it is affixed by an axle key (106) and wheel disc (105) respectively, intermediate pressure turbine axle (9) and cover shaft type low pressure turbine axle (13) respectively are rotationally connected by a bearing (60) and support (104), support (104) and differential coupling housing (5) Joint, wheel disc (105) is processed with a plurality of wedge shape raceways (107) with its circumferencial direction of upper edge, the adjacent side end face of support (104), a ball (103) and a spring (102) are housed in each wedge shape raceway (107), and described spring (102) is arranged on the outside of ball (103).

5. vortex combustion and steam turbine according to claim 1 is characterized in that: vortex venting gas appliance (53) is made of suction port (51), vortex venting gas appliance external admission mouth (50), vortex venting gas appliance relief opening (48), the 3rd solid-liquid body segregating unit (141), air guide volute (78) and strut (108) in vortex venting gas appliance gas-entered passageway (126), vortex venting gas appliance air inlet section (73), vortex venting gas appliance changeover portion (80), vortex venting gas appliance exhaust section (163), the vortex venting gas appliance; The 3rd solid-liquid body segregating unit (141) also comprises the 3rd tangential slit (174), the 3rd gas backstreaming pipe (175) and the 3rd solid-liquid body discharge tube (176); Vortex venting gas appliance air inlet section (73) is the annular constant speed volutes of two inlets, air guide volute (78) is divided into two the suction port of vortex venting gas appliance air inlet section (73), and be respectively suction port (51) and vortex venting gas appliance external admission mouth (50) in the vortex venting gas appliance, vortex venting gas appliance external admission mouth (50) is positioned at the outside of vortex venting gas appliance suction port (51), suction port (51) and vortex venting gas appliance external admission mouth (50) is all annular and join with the vortex venting gas appliance gas-entered passageway (126) of annular and to be communicated with in the vortex venting gas appliance, the inner edge of vortex venting gas appliance gas-entered passageway (126) is an involute shape and tangentially external with vortex venting gas appliance air inlet section (73) volute, and the outside of vortex venting gas appliance gas-entered passageway (126) is the prolongation transition wire of vortex venting gas appliance air inlet section (73) volute involute; Air guide volute (78) is arranged on the centre of interior suction port (51) of vortex venting gas appliance and vortex venting gas appliance external admission mouth (50), air guide volute (78) is supported by strut (108) and is affixed with vortex venting gas appliance air inlet section (73) volute, and the cross section of strut (108) is a blade-shaped; Vortex venting gas appliance changeover portion (80) is two Cylinder shape constructional elements, one end of two Cylinder shape constructional elements respectively with vortex venting gas appliance air inlet section (73) the tangent connection of volute, air guide volute (78) and vortex venting gas appliance air inlet section (73) volute that vortex venting gas appliance changeover portion (80) is corresponding with the tangent place of vortex venting gas appliance air inlet section (73) are save; The volute of vortex venting gas appliance exhaust section (163) is half toroidal, the other end of two Cylinder shape constructional elements of vortex venting gas appliance changeover portion (80) joins with two end faces of the hemicycle of vortex venting gas appliance exhaust section (163) annular volute respectively and is communicated with, vortex venting gas appliance exhaust section (163) is made up of ring (49) and the adjustable outer shroud of vortex venting gas appliance (47) in the vortex venting gas appliance, the adjustable outer shroud of vortex venting gas appliance (47) is arranged on the outside of ring (49) in the vortex venting gas appliance, array-type is provided with a plurality of vortex venting gas appliance relief openings (48) on interior ring of vortex venting gas appliance (49) and the adjustable outer shroud of vortex venting gas appliance (47) opposite position, and the adjustable outer shroud of vortex venting gas appliance (47) the interior ring of vortex venting gas appliance (49) relatively is slidingly matched vertically; Tangent the 3rd tangential slit (174) that is provided with a plurality of contrary airflow directions on vortex venting gas appliance air inlet section (73) the volute toroidal shell, the 3rd tangential slit (174) tangentially is communicated with the 3rd solid-liquid body segregating unit (141), the 3rd solid-liquid body segregating unit (141) is a ring housing structure, and a side that is arranged on vortex venting gas appliance air inlet section (73) volute toroidal shell is also mutually circumscribed; The 3rd gas backstreaming pipe (175) is made up of the comb of a plurality of the 5th blade-shaped pipes (118) of equidistant arrangement, be installed on the 3rd solid-liquid body segregating unit (141) toroidal shell, the one end extend into the center of the 3rd solid-liquid body segregating unit (141), the other end on the air-flow sense of rotation with vortex venting gas appliance air inlet section (73) the volute UNICOM of tangentially joining; The 3rd solid-liquid body discharge tube (176) tangentially is installed on the 3rd solid-liquid body segregating unit (141) toroidal shell, and direction tangential is tangential opposite on the 3rd solid-liquid body segregating unit (141) toroidal shell with the 3rd tangential slit (174).

6. according to claim 1,2 or 3 described vortex combustion and steam turbines, it is characterized in that: described turbocharger is grade separation type turbocharger (2), and grade separation type turbocharger (2) is made up of grade separation type turbocharger volute (129), grade separation type turbocharger suction port (45), grade separation type turbocharger relief opening (46), the first solid-liquid body segregating unit (121), grade separation type turbocharger gas-entered passageway (159) and grade separation type turbocharger exhaust passage (160); The first solid-liquid body segregating unit (121) comprises the first tangential slit (125), the first gas backstreaming pipe (124) and the first solid-liquid body discharge tube (123); Grade separation type turbocharger volute (129) is an annular constant speed volute, grade separation type turbocharger suction port (45) and grade separation type turbocharger gas-entered passageway (159) are all annular and are connected, the inner edge of grade separation type turbocharger gas-entered passageway (159) is an involute shape and tangentially external with grade separation type turbocharger volute (129), and the outside of grade separation type turbocharger gas-entered passageway (159) is the prolongation transition wire of grade separation type turbocharger volute (129) involute; Grade separation type turbocharger relief opening (46) is made up of the comb of the first blade-shaped pipe (92) of a plurality of equidistant arrangements, and the comb of the first blade-shaped pipe (92) of a plurality of equidistant arrangements is installed on the toroidal shell of grade separation type turbocharger volute (129); Grade separation type turbocharger gas-entered passageway (159) is crossed in grade separation type turbocharger exhaust passage (160), grade separation type turbocharger gas-entered passageway (159) and grade separation type turbocharger exhaust passage (160) are provided with a solid and intersect section, being arranged in the comb of the first blade-shaped pipe (92) of three-dimensional a plurality of equidistant arrangements of intersecting the section place is grade separation type turbocharger exhaust passage (160), and the comb that is arranged on the first blade-shaped pipe (92) of three-dimensional a plurality of equidistant arrangements of intersecting section is outward a grade separation type turbocharger gas-entered passageway (159); The comb of the first blade-shaped pipe 92 of the annular spaced set of grade separation type turbocharger relief opening (46) joins with the grade separation type turbocharger exhaust passage (160) of annular and is communicated with; Be respectively arranged with a position variant wedge-like body regulating controller (3) or deformation formula wedge-like body regulating controller (4) on grade separation type turbocharger gas-entered passageway (159) and the grade separation type turbocharger exhaust passage (160); With the tangent first tangential slit (125) that is provided with a plurality of contrary airflow directions of grade separation type turbocharger volute (129), the first tangential slit (125) tangentially joins with the first solid-liquid body segregating unit (121) and is communicated with, the first solid-liquid body segregating unit (121) is a ring housing structure, and a side that is arranged on grade separation type turbocharger (2) is also mutually circumscribed; The first gas backstreaming pipe (124) is made up of the comb of the 3rd blade-shaped pipe (116) of a plurality of equidistant arrangements, be installed on first solid-liquid body segregating unit (121) toroidal shell, the one end extend into the center of the first solid-liquid body segregating unit (121), the other end on the air-flow sense of rotation with grade separation type turbocharger volute (129) UNICOM of tangentially joining, the first solid-liquid body discharge tube (123) tangentially is installed on first solid-liquid body segregating unit (121) toroidal shell, and direction tangential is tangential opposite on first solid-liquid body segregating unit (121) toroidal shell with the first tangential slit (125).

7. according to claim 1,2 or 3 described vortex combustion and steam turbines, it is characterized in that: described turbocharger is override type turbocharger (20), and override type turbocharger (20) is made up of override type turbocharger volute (130), override type turbocharger suction port (72), override type turbocharger relief opening (66), the second solid-liquid body segregating unit (131), override type turbocharger gas-entered passageway (161) and override type turbocharger exhaust passage (162); The second solid-liquid body segregating unit (131) also comprises the second tangential slit (171), the second gas backstreaming pipe (172) and the second solid-liquid body discharge tube (173); Override type turbocharger volute (130) is an annular constant speed volute, override type turbocharger gas-entered passageway (161) and override type turbocharger suction port (72) are all annular and are connected, the inner edge of override type turbocharger gas-entered passageway (161) is an involute shape and tangentially external with override type turbocharger volute (130), and the outside of override type turbocharger gas-entered passageway (161) is the prolongation transition wire of override type turbocharger volute (130) involute; Override type turbocharger relief opening (66) is made up of the comb of the second blade-shaped pipe (115) of a plurality of equidistant arrangements, and the comb of the second blade-shaped pipe (115) of a plurality of equidistant arrangements is installed on override type turbocharger volute (130) toroidal shell; The comb of the second blade-shaped pipe (115) of the annular spaced set of override type turbocharger relief opening (66) joins with the override type turbocharger exhaust passage (162) of annular and is communicated with, and is respectively arranged with a position variant wedge-like body regulating controller (3) or deformation formula wedge-like body regulating controller (4) on override type turbocharger exhaust passage (162) and the override type turbocharger gas-entered passageway (161); With the tangent second tangential slit (171) that is provided with a plurality of contrary airflow directions of override type turbocharger volute (130), the second tangential slit (171) tangentially is communicated with the second solid-liquid body segregating unit (131), the second solid-liquid body segregating unit (131) is a ring housing structure, and a side that is arranged on override type turbocharger (20) is also mutually circumscribed; The second gas backstreaming pipe (172) is made up of the comb of the quaterfoil shape pipe (117) of a plurality of equidistant arrangements, be installed on second solid-liquid body segregating unit (131) toroidal shell, the one end extend into the center of the second solid-liquid body segregating unit (131), the other end on the air-flow sense of rotation with the tangential UNICOM of override type turbocharger volute (130); The second solid-liquid body discharge tube (173) tangentially is installed on second solid-liquid body segregating unit (131) toroidal shell, and direction tangential is tangential opposite on second solid-liquid body segregating unit (131) toroidal shell with the second tangential slit (171).

8. according to claim 1,2 or 3 described vortex combustion and steam turbines, it is characterized in that: described firing chamber is grade separation type eddy combustion chamber (93), and grade separation type eddy combustion chamber (93) is by grade separation type eddy combustion chamber volute (132), a plurality of grade separation type eddy combustions chamber dividing plates (100), grade separation type eddy combustion chamber suction port (29), grade separation type eddy combustion chamber relief opening (96), grade separation type eddy combustion chamber exhaust air collecting chamber (94), exhaust passage, grade separation type eddy combustion chamber (95), grade separation type eddy combustion chamber gas-entered passageway (136), at least one first fuel nozzle (133), at least one first igniter (134), at least one first water spout (135) and a plurality of wicker leaf shape pipe (120) are formed; Grade separation type eddy combustion chamber volute (132) is an annular constant speed volute, grade separation type eddy combustion chamber gas-entered passageway (136) and grade separation type eddy combustion chamber suction port (29) are all annular and are connected, the inner edge of grade separation type eddy combustion chamber gas-entered passageway (136) is an involute shape and tangentially external with grade separation type eddy combustion chamber volute (132), and the outside of grade separation type eddy combustion chamber gas-entered passageway (136) is the prolongation transition wire of grade separation type eddy combustion chamber volute (132) involute; The interior spaced set in grade separation type eddy combustion chamber (93) has a plurality of grade separation type eddy combustions chamber dividing plates (100), a plurality of grade separation type eddy combustions chamber dividing plates (100) are divided into multistage vertically with grade separation type eddy combustion chamber (93), every section grade separation type eddy combustion chamber (93) is made up of a grade separation type eddy combustion chamber mixed combustion section (90) and a grade separation type eddy combustion chamber mixing exhaust section (91), be provided with at least one first fuel nozzle (133) and at least one first igniter (134) in each grade separation type eddy combustion chamber mixed combustion section (90), be provided with at least one first water spout (135) in each grade separation type eddy combustion chamber mixing exhaust section (91), the centre of each grade separation type eddy combustion chamber dividing plate (100) is equipped with one first dividing plate air passing hole (101), and each section grade separation type eddy combustion chamber (93) forms a collar vortex through first dividing plate air passing hole (101) end-to-end; The collar vortex cross section grade separation type eddy combustion chamber volute (132) of grade separation type eddy combustion chamber (93) is provided with grade separation type eddy combustion chamber relief opening (96), grade separation type eddy combustion chamber relief opening (96) is positioned at the inboard of the terminal grade separation type eddy combustion chamber dividing plate (100) of each grade separation type eddy combustion chamber mixing exhaust section (91), the grade separation type eddy combustion chamber volute (132) in grade separation type eddy combustion chamber relief opening (96) outside is provided with grade separation type eddy combustion chamber exhaust air collecting chamber (94), grade separation type eddy combustion chamber relief opening (96) is communicated with grade separation type eddy combustion chamber exhaust air collecting chamber (94), grade separation type eddy combustion chamber exhaust air collecting chamber (94) joins with wicker leaf shape pipe (120) and is communicated with, wicker leaf shape pipe (120) joins with the exhaust passage, grade separation type eddy combustion chamber (95) of annular and is communicated with, wicker leaf shape pipe (120) is arranged on the corresponding grade separation type eddy combustion chamber volute (132) of grade separation type eddy combustion chamber suction port (29), at least one wicker leaf shape pipe (120) is established in every section grade separation type eddy combustion chamber (93), and the outside of wicker leaf shape pipe (120) is a grade separation type eddy combustion chamber gas-entered passageway (136); Be respectively arranged with a position variant wedge-like body regulating controller (3) or deformation formula wedge-like body regulating controller (4) on grade separation type eddy combustion chamber gas-entered passageway (136) and the exhaust passage, grade separation type eddy combustion chamber (95).

9. according to claim 1,2 or 3 described vortex combustion and steam turbines, it is characterized in that: described firing chamber is override type eddy combustion chamber (97), and override type eddy combustion chamber (97) is by override type eddy combustion chamber volute (137), a plurality of override type eddy combustions chamber dividing plates (138), override type eddy combustion chamber suction port (143), override type eddy combustion chamber exhaust air collecting chamber 144, override type eddy combustion chamber relief opening (99), exhaust passage, override type eddy combustion chamber (98), override type eddy combustion chamber gas-entered passageway (166), at least one second fuel nozzle (145), at least one secondary igniter (146) and at least one second water spout (147) are formed; Override type eddy combustion chamber volute (137) is an annular constant speed volute, override type eddy combustion chamber gas-entered passageway (166) and override type eddy combustion chamber suction port (143) are all annular and are connected, the inner edge of override type eddy combustion chamber gas-entered passageway (166) is an involute shape and tangentially external with override type eddy combustion chamber volute (137), and the outside of override type eddy combustion chamber gas-entered passageway (166) is the prolongation transition wire of override type eddy combustion chamber volute (137) involute; The interior spaced set in override type eddy combustion chamber (97) has a plurality of override type eddy combustions chamber dividing plates (138), a plurality of override type eddy combustions chamber dividing plates (138) are divided into multistage vertically with override type eddy combustion chamber (97), every section override type eddy combustion chamber (97) is made up of an override type eddy combustion chamber mixed combustion section (140) and an override type eddy combustion chamber mixing exhaust section (142), be provided with at least one second fuel nozzle (145) and at least one secondary igniter (146) in each override type eddy combustion chamber mixed combustion section (140), be provided with at least one second water spout (147) in each override type eddy combustion chamber mixing exhaust section (142), the centre of each override type eddy combustion chamber dividing plate (138) is equipped with a second partition air passing hole (139), and each section override type eddy combustion chamber (97) forms a collar vortex through second partition air passing hole (139) end-to-end; The position that is shaped as " C " font on override type eddy combustion chamber (97) the collar vortex cross section override type eddy combustion chamber volute (137) is provided with override type eddy combustion chamber relief opening (99), override type eddy combustion chamber relief opening (99) is positioned at the inboard of the terminal override type eddy combustion chamber dividing plate (138) of each override type eddy combustion chamber mixing exhaust section (142), the override type eddy combustion chamber volute (137) in override type eddy combustion chamber relief opening (99) outside is provided with override type eddy combustion chamber exhaust air collecting chamber (144), override type eddy combustion chamber relief opening (99) is communicated with override type eddy combustion chamber exhaust air collecting chamber (144), override type eddy combustion chamber exhaust air collecting chamber (144) joins with the exhaust passage, override type eddy combustion chamber (98) of annular and is communicated with, and is respectively arranged with a position variant wedge-like body regulating controller (3) or deformation formula wedge-like body regulating controller (4) on override type eddy combustion chamber gas-entered passageway (166) and the exhaust passage, override type eddy combustion chamber (98).

10. according to claim 1,2 or 3 described vortex combustion and steam turbines, it is characterized in that: described firing chamber is ring rotation firing chamber (71), and ring rotation firing chamber (71) are by ring rotation combustion chamber flame drum (164), ring (86) in the ring rotation firing chamber, ring rotation firing chamber outer shroud (42), fagging (87) before the ring rotation combustion chamber flame drum, ring rotation combustion chamber flame drum rear stay plate (88), compressorshaft gas compressor end core barrel (52), compressorshaft ratchet end core barrel (21), ring rotation firing chamber gas-entered passageway (167), ring rotation exhaust combustion chamber passage (168), at least one the 3rd fuel nozzle (148), at least one is firearm (149) and at least one the 3rd water spout (150) composition thirdly; Be provided with ring rotation combustion chamber flame drum (164) between ring (86) and ring rotation firing chamber outer shroud (42) in the ring rotation firing chamber, ring rotation combustion chamber flame drum (164) is made up of ring (43) and ring rotation combustion chamber flame drum outer shroud (40) in the ring rotation combustion chamber flame drum, the preceding fagging (87) of the front end of the front end of ring (86) and ring rotation combustion chamber flame drum (164) and ring rotation combustion chamber flame drum is affixed in the ring rotation firing chamber, the rear end and the ring rotation combustion chamber flame drum rear stay plate (88) of the rear end of ring (86) and ring rotation combustion chamber flame drum (164) are affixed in the ring rotation firing chamber, and fagging (87) and ring rotation combustion chamber flame drum rear stay plate (88) are packed in respectively on the compressorshaft (58) of gas compressor (1) before the ring rotation combustion chamber flame drum; Ring (43), ring rotation combustion chamber flame drum outer shroud (40), the preceding fagging (87) of ring rotation combustion chamber flame drum and ring rotation combustion chamber flame drum rear stay plate (88) are lamination interlayer small structure in the ring rotation combustion chamber flame drum; Ring rotation combustion chamber flame drum (164) is divided into five sections vertically, 3/5ths sections of the ring rotation combustion chamber flame drum (164) of close gas compressor (1) rear end are ring rotation firing chamber mixed combustion section (151), 2/5ths sections of the ring rotation combustion chamber flame drum (164) of close high pressure turbine (7) front end are ring rotation firing chamber mixing exhaust section (152), be provided with thirdly firearm (149) of at least one the 3rd fuel nozzle (148) and at least one in the ring rotation firing chamber mixed combustion section (151), be provided with at least one the 3rd water spout (150) in the ring rotation firing chamber mixing exhaust section (152), compressorshaft gas compressor end core barrel (52) is the conveyance conduit of ring rotation firing chamber fuel, compressorshaft ratchet end core barrel (21) is the conveyance conduit of ring rotation high combustion chamber pressures clean water, compressorshaft gas compressor end core barrel (52) joins with at least one the 3rd fuel nozzle (148) and is communicated with, and compressorshaft ratchet end core barrel (21) joins with at least one the 3rd water spout (150) and is communicated with; Ring rotation firing chamber gas-entered passageway (167) is arranged on the outside of ring rotation firing chamber outer shroud (42) and adjacent with gas compressor (1) for annular, ring rotation exhaust combustion chamber passage (168) is respectively arranged with a position variant wedge-like body regulating controller (3) or deformation formula wedge-like body regulating controller (4) for annular is arranged on the outside of ring rotation combustion chamber flame drum outer shroud (40) and adjacent with high pressure turbine (7) on ring rotation firing chamber gas-entered passageway (167) and the ring rotation exhaust combustion chamber passage (168).

11. according to claim 1,2 or 3 described vortex combustion and steam turbines, it is characterized in that: described firing chamber is tubular revolving combustor (54), and tubular revolving combustor (54) is by front end axle (165), rear end axle (67), tubular revolving combustor frame (89), tubular revolving combustor burner inner liner (41), tubular revolving combustor front end axle center pipe (155), axle center, tubular revolving combustor rear end pipe (75), tubular revolving combustor gas-entered passageway (169), tubular revolving combustor exhaust passage (170), two end axle faggings (84), two burner inner liner indent end plates (85), a plurality of hollow stator blades (81), at least one the 4th fuel nozzle (156), at least one the 4th igniter (157) and at least one the 4th water spout (158) are formed; Be provided with tubular revolving combustor burner inner liner (41) in the chamber of tubular revolving combustor frame (89), the front-end and back-end of tubular revolving combustor burner inner liner (41) respectively are provided with a burner inner liner indent end plate (85), two burner inner liner indent end plates (85) are affixed with front end axle (165) and rear end axle (67) respectively at the two ends of tubular revolving combustor burner inner liner (41), front end axle (165) and rear end axle (67) respectively are provided with an end axle fagging (84) perpendicular to two burner inner liner indent end plates (85) end face, two end axle faggings (84) respectively with front end axle (165), rear end axle (67) and two burner inner liner indent end plates (85) are affixed, front end axle (165) is an axon with the compressorshaft (58) of gas compressor (1), rear end axle (67) is by the end transmission joint of ratchet type overrunning clutch (57) with the high pressure turbine axle (6) of high pressure turbine (7), front end axle (165) and compressorshaft (58) are provided with tubular revolving combustor front end axle center pipe (155), tubular revolving combustor front end axle center pipe (155) joins with at least one the 4th fuel nozzle (156) and is communicated with, rear end axle (67) is provided with axle center, tubular revolving combustor rear end pipe (75), and axle center, tubular revolving combustor rear end pipe (75) joins with at least one the 4th water spout (158) and is communicated with; Tubular revolving combustor burner inner liner (41), two end axle faggings (84) and two burner inner liner indent end plates (85) are lamination interlayer small structure; Tubular revolving combustor burner inner liner (41) evenly is divided into five sections vertically, 3/5ths sections of the tubular revolving combustor burner inner liner (41) of close gas compressor (1) rear end are tubular revolving combustor mixed combustion section (153), 2/5ths sections of the tubular revolving combustor burner inner liner (41) of close high pressure turbine (7) front end are tubular revolving combustor mixing exhaust section (154), be provided with at least one the 4th fuel nozzle (156) and at least one the 4th igniter (157) in the tubular revolving combustor mixed combustion section (153), be provided with at least one the 4th water spout (158) in the tubular revolving combustor mixing exhaust section (154); Tubular revolving combustor gas-entered passageway (169) is arranged on the outside of tubular revolving combustor frame (89) and adjacent with gas compressor (1), and tubular revolving combustor exhaust passage (170) is arranged on the outside of tubular revolving combustor burner inner liner (41) and adjacent with high pressure turbine (7); Intersect a plurality of hollow stator blades (81) that are provided with equidistant arrangement on the section at annular space between tubular revolving combustor burner inner liner (41) and the tubular revolving combustor frame (89) and tubular revolving combustor exhaust passage (170), be tubular revolving combustor exhaust passage (170) in each hollow stator blade (81), each hollow stator blade (81) is outer to be compressed air channel; Be respectively arranged with a position variant wedge-like body regulating controller (3) or deformation formula wedge-like body regulating controller (4) on tubular revolving combustor gas-entered passageway (169) and the tubular revolving combustor exhaust passage (170).