WO2008138221A1

WO2008138221A1 - Intercooling equipressure heat-of-absorption type air turbine

Info

Publication number: WO2008138221A1
Application number: PCT/CN2008/000920
Authority: WO
Inventors: Peizhou Han
Original assignee: Peizhou Han
Priority date: 2007-05-09
Filing date: 2008-05-09
Publication date: 2008-11-20
Also published as: CN101050714A

Abstract

An intercooling equipressure heat-of-absorption type air turbine comprises an intercooler (14), a heater (36), a boiler (41), an air compressor (8) and an air turbine (28) connected with a main shaft (26). A distribution device (48) carrying out equal pressure decalescence is mounted between the heater (36) and the air turbine (28). Intercooling decreases directly compression work consumption of the air compressor (8) and provides the largest temperature difference for equal pressure decalescence. All heat in fuel gas of the boiler (41) is basically absorbed during equal pressure decalescence carrying out separately, thus increasing decalescence efficiency of the heater (36) in vast scale. When the boiler (41) is adopted as an exterior heat source and the exchanging heat of intercooling and the air turbine (28) is led to the boiler (41) in combustion together, the loss heat is recycled and the circle thermal efficiency is improved further. The turbine is suitable to be made into a more powerful one and use coal as fuel, and it is feasible to be used as power device of power plant.

Description

Intercooled isobaric heat-absorbing air turbine

The present invention relates to an air turbine, and more particularly to an intercooled isobaric heat engine for a power plant. Background technique

Steam power plants consisting of boilers, steam turbines and condensers are widely used in power plants for power generation in power plants due to their high power and reliable operation. However, in the steam power plant, the steam is re-converted into water due to the steam entering the condenser after the work of the steam turbine, and a large amount of latent heat in the steam is scattered to the outside to generate a large heat loss. And the application number is

In the medium-cooling isobaric heat-absorbing heat engine described in "200710086603.8", although the vapor condensation heat loss in the steam cycle is avoided by the isothermal heat absorption by intermediate cooling and the use of air as the working fluid, the isothermal heat absorption due to the medium-cooling A hot air machine is an engine that uses a piston to perform work. When making a power unit with a higher power, the piston type power conversion mechanism is obviously not as small as a steam turbine. Summary of the invention

The object of the present invention is to provide an intercooled isobaric heat-absorbing air turbine in combination with a gas turbine such an impeller power conversion mechanism, while retaining a core isobaric heat absorbing structure of an intermediate-cooled isobaric heat-absorbing heat engine. The air turbine not only has high heat absorption and utilization efficiency, but also can be made into a power plant with a larger power by using a gas turbine, thereby making it more suitable for power generation in a power plant.

The medium-cooling isostatic endothermic air turbine of the present invention comprises an intercooler, a heater, a boiler, a compressor and a gas turbine connected via a main shaft, the heater is arranged in the boiler, or the high-temperature exhaust or exhaust arranged in other heat sources Inside the liquid pipe. The utility model is characterized in that: the utility model further comprises: a plurality of gas distribution devices formed by the outer casing and the rotary cylinder body therein, wherein the rotary cylinder body is mounted on the central shaft fixedly connected with the outer casing, and the upper rotary shaft body is respectively arranged annularly around the central axis. a small auxiliary cylinder with a cold vent and a large auxiliary cylinder with a hot vent on the other side, and a correspondingly sized gas piston in the primary and secondary cylinders is connected to the swash plate on the central shaft via a connecting rod, rotating The cylinder is driven by the central gear on the main shaft through the gear on the main shaft; when the rotary cylinder rotates, the cold vent on the small auxiliary cylinder can be respectively connected with the inflation port and the ventilation outlet provided on the small valve disc on the side of the outer casing. Communication, big The heat vents on the auxiliary cylinders can respectively communicate with the gas inlet and outlet ports provided on the large valve disc on the other side of the outer casing; the outlet passage of the compressor passes through the intermediate cooler and the small valve disc of the gas distribution device The gas inlets on the upper side are connected, and the gas outlet of the small valve disc is connected to the gas exchange inlet on the large valve disc through the pipeline, the heater and the heat insulating tube, and the gas outlet of the large valve disc is led to the gas turbine through the pressure heat insulating tube In the case of using the boiler as an external heat source, the intercooler is disposed in an air cooling jacket that exchanges heat in a countercurrent manner, and the cooling air outlet of the cooling jacket is led to a corresponding air inlet of the boiler through a duct provided with a blower.

In order to make the size of the gas distribution piston adopt a more powerful transmission structure, in the gas distribution device, the large gas distribution pistons in the rotary cylinder body are respectively connected with the corresponding small gas distribution piston through the connecting beam, and the connecting beam is connected. The inner side has a concave portion that avoids the swash plate, and a sliding rail is disposed on an outer side surface of the connecting beam, and a seat rail is disposed at a corresponding position on the inner side surface of the rotating cylinder connecting shell, and is installed between the seat rail and the sliding rail A roller row composed of a cage and a roller; a plurality of single-row mounting shafts arranged on both sides in a double row or in the middle, and the same intermediate gears on the shaft, the gears and the seat rails Engaged with the corresponding rack provided on the slide rail.

In a specific arrangement of the gas distribution device, the gas distribution device may be arranged symmetrically or annularly around the main shaft, and the gas outlet on the gas inlet is opposite to the gas inlet of the gas turbine and communicated via the pressure heat insulating tube. A set of the same gas distribution device may be further disposed on the outer side of the symmetrical or annular gas distribution device, and the gas distribution device and the inner gas distribution device are installed at a certain angle, so that the corresponding gas outlets respectively are respectively arranged The elongated pressure insulated pipe passing through the gap of the inner gas distribution device opens to the intake port of the gas turbine, and the elongated main shaft drives the gear on the rotary cylinder in the gas distribution device through the outer center gear.

In an air turbine with closed circulation, the compressor is arranged at the rear of the gas turbine, and the exhaust port of the gas turbine is arranged opposite to the inlet of the compressor, and the two ports are connected by a communication path, and are arranged in the communication channel. There is an air preheater, and the exhaust vent of the preheater is connected to the corresponding air inlet of the boiler through a pipe provided with a blower.

For the specific structure of the air preheater provided in the communicating duct, the air preheater is composed of a number of heat absorbing flat tubes which have a suitable length and are arranged along the exhaust flow in the ring table. In the communicating channel, each of the heat absorbing flat tubes is radially arranged in a circular cross-section in the annular communication channel, and adjacent heat absorbing flat tubes are connected by a plurality of heat absorbing sheets arranged in the direction of the air flow, each endothermic The flat tubes are connected by a heat absorbing sheet to form a ring-shaped integral preheater structure, and the front end and the tail portion of each of the heat absorbing flat tubes are streamlined.

In an open air turbine, the exhaust passage of the gas turbine leads to the phase of the boiler It should be installed in the air vent, and a venting valve that is opened when low power is provided on the exhaust passage.

In order to recover the heat in the exhaust of the gas turbine, the exhaust port of the gas turbine is led to the outside through an exhaust passage provided with an air preheater, and the exhaust port of the air preheater is led to the boiler through a pipe provided with a blower. Corresponding air inlets.

In order to allow the air turbine to increase the transmission power in an internal combustion mode, a bypass line with a combustion chamber is provided at the periphery of the pressure insulated pipe connected to the gas outlet of the gas distribution device, and the inlet and pressure insulation of the bypass pipe are provided. An oscillating valve is arranged between the tubes. When the combustion chamber is burning, the oscillating valve swings from the position of the closed bypass line to the pressure insulated tube. Of course, a simpler combustion chamber arrangement can also be adopted, and an afterburner is directly arranged on the pressure heat insulating pipe connected to the gas outlet of the gas distribution device, and the telescopic fuel injector is extended when the fuel is injected. Into the afterburner.

The medium-cooling isobaric heat-absorbing air machine of the invention is developed on the basis of retaining the medium-pressure heat-absorbing core structure of the medium-cooling isobaric heat-absorbing heat engine, and the power device still has the highest heat absorption efficiency, and can The heat of the high temperature airflow in the external heat source is basically exhausted. When the air turbine of the present invention uses a boiler as an external heat source, since the heat-dissipating air of the intercooler can be introduced into the boiler to participate in combustion, the heat of compression generated in the compressor can be recovered, thereby greatly improving the present invention. The thermal efficiency of such an external combustion air turbine. The highest cycle thermal efficiency, while also allowing the turbine to generate a large amount of power, these advantages make the air turbine of the present invention particularly suitable for power plant power generation, thereby creating a significant reduction in power plant fuel consumption and reduction of carbon dioxide greenhouse gas emissions. condition.

In addition, in the air turbine of the present invention, the transmission mechanism adopted for the gas distribution piston in the gas distribution device is improved, and the connecting beam between the large and small gas distribution pistons is connected to the seat on the rotating shell through the roller row and the rotating cylinder block. The rail contact makes the large and small gas distribution pistons and the connecting beam not to generate too much frictional resistance and can work reliably under the action of large centrifugal force. Since the three types of moving parts of the piston type gas distribution device, the compressor and the gas turbine in the air turbine of the present invention can be stably operated for a long time, it is very necessary as a power plant of the power plant. DRAWINGS

The air turbine of the present invention will be further described in detail below with reference to the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a cross-sectional view showing a first embodiment of a cold isostatic endothermic air turbine of the present invention. Figure 2 is a partially enlarged cross-sectional view showing the connecting beam and the roller row provided in the air turbine shown in Figure 1. Figure 3 is a plan view of the roller row shown in Figure 2

Figure 4 is a side cross-sectional view of the preheater in the air turbine of Figure 1.

Figure 5 is a cross-sectional view taken along line A-A of Figure 4

Fig. 6 is a schematic view showing the arrangement of a second embodiment of a cold isostatic endothermic air turbine according to the present invention.

Fig. 7 is a flow chart showing the heat utilization and loss of the cold isostatic endothermic air turbine of the present invention. Figure 8 is a cross-sectional view showing a third embodiment of the cold isostatic endothermic air turbine of the present invention. detailed description

1 to 5 show a first embodiment of the cold isostatic endothermic air turbine of the present invention. The air turbine includes an intercooler 14, a heater 36, a boiler 41, a compressor 8 and a gas turbine 28 connected via a main shaft 26, and the heater 36 is disposed in a boiler 41 using solid fuel. When using other external heat sources (such as nuclear reactors), the heater is located in the high temperature exhaust or drain line of this external heat source. In order to perform the heat absorption process in the isobaric state, a gas distribution device 48 is disposed between the intercooler 14 and the heater 36. The gas distribution device is composed of a casing 49 and a rotating body 76 therein, and the rotating cylinder is mounted The central shaft 62 to which the outer casing 49 is fixedly coupled is provided with a small sub-cylinder 82 having a cold vent 83 and a large sub-cylinder 92 having a heat vent 93 on the other side, which are annularly arranged around the central axis. The corresponding sized valve pistons 95, 85 in the primary and secondary cylinders 92 and 85 are coupled to the swash plate 66 on the central shaft 62 via a connecting rod. A gear 77 is provided on the rotary cylinder 76, and a sun gear 27 on the main shaft 26 drives the gear 77 to rotate the rotary cylinder. When the rotary cylinder 76 rotates, the cold vents 83 on the small auxiliary cylinders 82 can respectively communicate with the inflation ports 51 and the ventilation outlets 53 provided on the small valve disc 50 on the side of the outer casing 49; The heat vents 93 are respectively communicable with the ventilation inlet 58 and the outlet 60 provided on the large valve disc 56 on the other side of the casing.

The overall arrangement of the components of the cold isostatic endothermic air turbine of the present invention is as shown in Fig. 1. The air outlet passage 1 of the compressor 8 is connected to the inflation port 51 of the small valve disc 50 of the air distribution device via the intercooler 14. The ventilation outlet 53 of the small valve disc communicates with the ventilation inlet 58 of the large valve disc 56 via the line 55, the heater 36 and the heat insulating tube 38, and the air outlet 60 of the large valve disc is connected to the pressure insulating tube 61. To the intake of the gas turbine 28. Since the boiler is used as an external heat source in the present embodiment, in order to fully recover the heat of compression generated by the compressor 8, the intercooler 14 behind the compressor is disposed in the air cooling jacket 18 that exchanges heat in a countercurrent manner, and is cooled. The heat dissipating air outlet 21 of the sleeve passes through the duct 23 provided with the blower 24 to the phase of the boiler 41 Should enter the air outlet 42. The higher temperature dissipating air obtained by the countercurrent intercooling heat exchange is introduced into the boiler to participate in the combustion, so that the heat loss generated by the intermediate cooling is mostly recycled, and the compression work consumed by the compressor due to the intermediate cooling is large. The magnitude is reduced. Since better intermediate cooling is beneficial to reduce the compressor's compression work consumption, and also increases the heat absorption temperature difference of the heater 36 in the boiler 41, it is also possible to set a corresponding water-cooled cryogenic after the intercooler 14 Intercooler (not shown).

In the first embodiment shown in FIG. 1, the compressor 8 is disposed behind the gas turbine 28, and the exhaust port of the gas turbine is disposed opposite to the intake port of the compressor 8, and the two ports are communicated through the communication passage 35. Connected to form a closed air circulation system. In order to recover the exhaust heat of the gas turbine 28 and improve the intake state of the compressor 8, an air preheater 104 is further disposed in the communication passage 35, and the exhaust port 107 of the preheater is connected to the pipeline provided with the blower 109. 108 leads to a corresponding air inlet 43 of the boiler 41. Obviously, in order to obtain a higher temperature preheating air, the exhaust flow of the air preheater 104 and the gas turbine 28 are heat exchanged in a countercurrent manner, and the blower 109 provided should also have a speed control function so as to be in power. When the temperature of the exhaust gas is lowered, the cooling air volume is adjusted accordingly.

In the above arrangement, although the heat of compression of the compressor 8 and the exhaust heat of the gas turbine 28 can be sufficiently recovered by the air cooling jacket 18 and the air preheater 104, in practice, since the combustion efficiency of the boiler 41 is in contact with the air There is a corresponding correspondence between the gas volume, and the combustion efficiency is also lowered when the intake air amount is too large. Therefore, a corresponding bleed valve (not shown) should be provided on the pipe 23 and the pipe 108 to allow the intake air to enter the boiler. The total amount can be controlled by mediation.

During operation of the intercooled isostatic endothermic air turbine of the present invention, the intermediate cooling process performed by the intercooler 14 and the isostatic endothermic process by the heater 36 are separated by the gas distribution device 48 and The two cycles of mutual promotion, the lower the temperature of the compressed air after the intermediate cooling, the less the compression work consumed by the compressor 8, and the more advantageous it is for the heater 36 to absorb more heat from the boiler. In order to allow the gas entering and exiting the large and small cylinders to smoothly flow, in the suction and exhaust strokes of the small auxiliary cylinder 82, the cold vents 83 of the small auxiliary cylinders can be exchanged with the inflation ports 51 on the small valve disc 50 of the outer casing, respectively. The gas outlet 52 communicates at an angle close to 180° (the cold vent cannot communicate both the inflation port and the ventilation outlet). During the intake of the master cylinder 92, the heat vent 93 of the master cylinder communicates with the air inlet 58 on the large valve disc 56 at an angle of 180. . In the exhaust process of the large auxiliary cylinder 92, the air outlet 60 on the large valve disc can be connected to the heat vent 93 when the large air distribution piston 95 moves upward from the bottom dead center, and the air outlet can be appropriately reduced. The angle of 60, let the large gas piston 95 to the working gas in the large auxiliary cylinder 92 First, a certain degree of compression is performed, and then the work gas with increased pressure is flushed out from the opened air outlet 60 through the heat vent to push the turbine 28 to work externally. Of course, the angle of the air outlet 60 cannot be reduced too much to avoid the difficulty of sealing and increasing the mechanical load on the swash plate.

Since the medium-cooled isobaric heat-absorbing air turbine of the present invention is usually made into a large power when used in a power plant, in order to adapt to the large flow characteristics of the gas turbine 28, in addition to increasing the size of the gas distribution device, mainly By increasing the number of gas distribution devices. The gas distribution device 48 is disposed symmetrically about the main shaft 26 (two units) or a ring type, and the air outlet 60 on the air inlet port 60 is opposed to the air inlet of the gas turbine 28 and communicates through the pressure heat insulating tube 61. If the arrangement still fails to achieve the required gas delivery volume, a set of the same gas distribution device (not shown) may be further disposed on the outer side of the symmetric or annular arrangement gas distribution device 48, and the The group air distribution device is installed at a certain angle from the inner gas distribution device, so that the corresponding air outlets 60 are respectively connected to the air intake of the gas turbine 28 through the elongated pressure heat insulating tubes passing through the gaps of the inner gas distribution device. mouth. At the same time, in order to drive the outer air distribution device, the elongated main shaft 26 also drives the gear 77 on the rotary cylinder 76 in the outer gas distribution devices through the outer center gear.

In the gas distribution device 48, in the structure of the cylindrical transmission mechanism, the respective gas distribution pistons 95 of the rotary cylinder 76 are integrally connected to the corresponding small gas distribution pistons 85 via the connecting beams 86, and the swash plate 66 is connected through the connection. The rod 96 is connected to the large valve piston, and the inside of the connecting beam 86 has a recessed portion 87 that avoids the swash plate 66. In order to adapt the rotating cylinder to a higher rotational speed and reduce the frictional resistance caused by the large centrifugal force of the gas distribution piston and the connecting beam, as shown in Fig. 2, a sliding rail 88 is provided on the outer side surface of the connecting beam, and A seat rail 80 is provided at a corresponding position on the inner side surface of the rotary cylinder connecting casing 78, and a roller row 98 is added between the sliding rail of the connecting beam and the seat rail of the connecting casing. The roller row 98 is composed of a retainer 100 and a roller 99 (see FIG. 3). The roller row 98 can be held in a predetermined moving position during reciprocal movement with the connecting beam 86, and is disposed on the retainer 100. There are several Hanban mounting shafts 102 arranged in two places (the mounting shafts can also be arranged in the middle for single row arrangement). The mounting shafts are equipped with the same intermediate gears 101, which are provided on the seat rails and the slide rails. The respective racks 81, 89 are engaged. The roller row 98 is only provided to overcome the large centrifugal force, and the two sides of the connecting beam 86 can be formed into a sliding rail and matched with the corresponding rail surface on the connecting shell, so that the size gas distribution piston can only pass The piston ring is in contact with the inner wall of the cylinder without having to lubricate between the two to keep the internal circulating air clean. Due to the heavy mass of the large gas distribution piston 95 side, in practice, a certain balance weight should be added to the small gas distribution piston side. For the air preheater 104 disposed in the communication passage 35 between the gas turbine 28 and the compressor 8, as shown in Figs. 4 and 5, a structural mode which is advantageous for reducing the airflow resistance is adopted. The heat exchanger 104 is composed of a number of heat absorbing flat tubes 1 12 having appropriate lengths and flowing in the direction of the exhaust gas in the annular communication passages 35, each of which has a cross section in a ring shape. The communicating channels are radially arranged, and the adjacent heat absorbing flat tubes 1 12 are connected by a plurality of supporting heat absorbing sheets 1 13 arranged in the direction of the exhaust gas flow. The heat absorbing flat tubes described above are connected by a heat absorbing sheet to form a ring-shaped integral preheater structure, and the front end and the tail portion of each of the heat absorbing flat tubes have a streamline shape.

Figure 6 is a perspective view of a second embodiment of a cold isostatic endothermic air turbine of the present invention. Unlike the first embodiment, in the second embodiment, the exhaust passage 34 of the gas turbine 28 is directed to the boiler 41. The corresponding air inlet 43 allows the air discharged by the gas turbine with a certain amount of residual heat to enter the boiler to participate in combustion, so that the heat in the air is fully absorbed to reduce the fuel consumption in the boiler. In an air turbine in which the output power frequently changes, a bleed valve (not shown) is further disposed on the exhaust passage 34 to open the valve to properly deflate when the power is lowered, and the combustion heat of the fuel 47 is adjusted in conjunction with the boiler 41. . Of course, a bleed valve (not shown) is also provided on the conduit 23 in communication with the air cooling jacket 18 to control the amount of intake air entering the boiler and to provide the highest temperature in the exhaust passage 34 or conduit 23. The air enters the boiler 41 in order to recover more heat and heat from the circulation. The air turbine of Figure 6 is in an open loop arrangement.

The working process of the cold isostatic endothermic air turbine of the present invention will be described below with reference to the second embodiment of FIG. 6. The air turbine includes three processes of isothermal compression, isostatic heat absorption and expansion work, among which isothermal compression and Isobaric endotherm is a mutually circulated process that is separated from each other.

(1) Isothermal compression process

The compressor 8 compresses the air sucked from the inlet 10, and the low-temperature compressed air (below 60 ports) generated by the intercooler 14 enters the small state in the inhalation state along the outlet passage 11 in the direction of the arrow 17 through the inflation port 51. Auxiliary cylinder 82. When the small gas cylinder of the small sub-cylinder 82 is lined up to the bottom dead center and the small sub-cylinder filled with the low-temperature compressed air is also rotated through the inflation port 51, the isothermal compression process ends.

The isothermal compression causes the compression heat generated by the compressor 8 during the compression process to be directed by the intercooler 14 to the air cooling jacket 18, so that the temperature and pressure of the compressed air at the end of the compression state are greatly reduced. Reduced compressed air temperature provides maximum for the isobaric heat absorption process The temperature difference; while the pressure of the compressed air is reduced, the compression work consumed by the compressor is greatly reduced, and the compression state of the compressor is improved.

When the boiler 41 is used as the external heat source of the heater 36, the heat of compression generated by the isothermal compression is not dissipated, but the air cooling jacket 18 of the countercurrent heat exchange is sufficiently recovered, and then the temperature is raised. Air is introduced into the boiler 41 by the blower 24 to participate in combustion, thereby correspondingly reducing fuel consumption.

(2) Isobaric endothermic process

This process is realized by the exhaust of the small auxiliary cylinder 82 and the suction process of the large auxiliary cylinder 92. When the small auxiliary cylinder 82 filled with the low temperature compressed air starts to exhaust with the rotation of the rotary cylinder, the cold on it The vent port 83 also communicates with the ventilating outlet 53, and the upwardly moving small valve piston 85 discharges the low temperature compressed air in the small sump into the heater 36 in the direction of the arrow 39, and is heated by the combustion gas in the boiler 41. At the same time, the large valve piston 95 in the other side large-cylinder 92 communicated by the heater is moving to the bottom dead center to inhale, and the high-temperature work air heated by the heater 36 (600 ° C) The first auxiliary cylinder 92 is filled from the ventilation inlet 58 via the heat insulating tube 38 in the direction of the arrow 40. Since the volume of the large auxiliary cylinder is larger than that of the small auxiliary cylinder, the volume of the low temperature compressed air heated by the heater can be expanded correspondingly in the large auxiliary cylinder, so that the gas pressure in the heating circulation system does not rise, so that the heat absorption process is The isobaric state is carried out. After the small valve piston in the small auxiliary cylinder reaches the top dead center, the large gas distribution piston in the large auxiliary cylinder goes to the bottom dead center and is filled with the high temperature working air, the isobaric heat absorption process ends.

Due to the isothermal heat absorption, the temperature of the low-temperature compressed air that has just entered the heater 36 does not rise, and the corresponding heat can be absorbed from the combustion gas which has been rapidly flowing through the periphery of the heater, so that the boiler generates The heat in the combustion gas can be substantially exhausted, thereby increasing the utilization efficiency of the fuel heat and increasing the heat absorption potential of the heater.

During the isobaric heat absorption process, in the large and small cylinders that are simultaneously connected, the large gas distribution piston 95 is pushed to perform the corresponding work due to the difference in the area of the large and small gas distribution pistons, and at least the rotation cylinder 76 itself can be rotated. The driving force.

(3) Expansion work process

After the large-pressure cylinder 92, which is at the end of the isostatic endothermic process and is filled with the high-temperature work air, is turned to the position communicated with the air outlet 60, the large air distribution piston 95 therein discharges the high-temperature work air in the direction of the arrow 94. The gas turbine 28 drives the turbine to rotate, and drives the compressor 8 and the rotary cylinder 76 to operate and work externally. The air still discharged from the gas turbine 28 and still having a certain temperature enters the boiler 41 through the exhaust passage 34 in the direction of the arrow 33 to participate in combustion, and the heat in the exhaust of the turbine is exhausted. The amount is directly recovered.

In the isothermal compression, isobaric heat absorption and expansion work performed by the above air turbine, the favorable factors for improving the thermal efficiency mainly include two aspects. First, the isothermal heat absorption can basically exhaust the heat generated by the boiler, and then Is isothermal compression, which not only minimizes the compression work consumed by the compressor, but also the heat dissipated during the compression process and the exhaust heat of the gas turbine can be recovered into the boiler to allow the heat lost by the air turbine of the present invention. Very few.

The heat utilization and loss flow diagram of the cold isostatic endothermic air turbine in the process of the present invention is shown in Fig. 7. In practice, since the total intake air amount entering the boiler has an optimum range, the intercooler generates The cooling air and the hot air discharged from the gas turbine will not enter the boiler completely, but in the case that the highest temperature hot air generated by the intercooler or the gas turbine can enter the boiler more, the boiler is cooled from the intermediate cooling and the exhaust heat of the turbine. The heat recovered can reach 32%. When the heat of the fuel added to the boiler is 100%, and after the heat loss of the boiler is reduced by 15%, the heat power obtained by the gas turbine is 117%. After removing the power consumption of the compressor and the intermediate cooling loss, the shaft output of the gas turbine The power can account for 70% of the fuel's heat, which is 70% effective efficiency of the air turbine, making it the most efficient external combustion power unit. Since the air turbine of the present invention uses the impeller-type compressor and the gas turbine for compression and work, it is suitable for large-scale development, and can completely replace the steam power system in the ordinary power plant, and provides a powerful means for greatly reducing power consumption and coal consumption. Technical Support.

Figure 8 illustrates a third embodiment of the cold isostatic endothermic air turbine of the present invention. The air turbine of this embodiment also employs an open cycle, and the exhaust port of the gas turbine 28 is provided with an air preheater. The exhaust passage 34 of the air passage 104 is open to the atmosphere, and the exhaust port of the air preheater is led to the corresponding air inlet 43 of the boiler 41 via a line 108 provided with a blower 109 to recover heat in the exhaust of the gas turbine 28.

In the present embodiment, a bypass line 70 with a combustion chamber 68 is provided at the periphery of the pressure heat insulating tube 61 connected to the air outlet 60 of the gas distribution device, and the inlet and the pressure heat insulating tube of the bypass line are provided. An oscillating valve 72 is provided between 61, so that when the output power is required to be increased for a short period of time, and the combustion chamber is subjected to fuel injection combustion, the matching oscillating valve 72 will be closed from the state of the bypass line 70, correspondingly to the pressure. The inside of the insulated pipe 61 is swung (as indicated by the dotted swing valve position in the figure), and the combustion chamber 68 is allowed to obtain a flow of hot air required for combustion. This structural arrangement is a composite circulation method involving external combustion and internal combustion and external combustion.

Since the air turbine power range of the composite cycle is larger, in order to allow the air preheater 104 behind the gas turbine 28 to sufficiently recover the heat contained in the exhaust gas, the blast is performed. The air conditioner 109 is controlled by the speed regulating device 115, and according to the temperature change information of the temperature sensor 1 16 provided on the exhaust passage 34, the rotational speed of the air blower can be increased correspondingly at a high power, so that the airflow in the air preheater flows rapidly. In order to recover more heat from the high temperature exhaust gas in the exhaust passage.

As a simplified and improved design of the third embodiment, an afterburner (not shown) may be directly disposed on the pressure heat insulating pipe 61 connected to the air outlet 60 of the air distribution device, and a telescopic type is also provided. The fuel injector is configured to allow the fuel injector to extend into the afterburner fuel injection combustion as needed to increase the power output of the air turbine for a short period of time.

The three different embodiments of the cold isostatic endothermic air turbine of the present invention are fully described above. Since the air turbine of the present invention generates little heat loss during operation, it will become the most fuel-efficient power plant. Power generation power plants have created the necessary conditions to significantly reduce greenhouse gas emissions from carbon dioxide. Because of the small amount of waste heat generated, this new type of power plant does not require a cooling tower used in ordinary steam power plants, nor does it emit a large amount of heat into the atmosphere or sea water. The use of air as a working medium can also get rid of the dependence on water and minimize the limitation of the power plant's location. Of course, the air turbine of the present invention is not only suitable as a power plant for a power plant, but is also fully operable as a power unit in large and medium-sized ships and ground power sources.

Claims

Rights request

1. An intercooled isostatic endothermic air turbine comprising an intercooler (14), a heater (36), a boiler (41), a compressor (8) and a gas turbine connected via a main shaft (26) ( 28), the heater (36) is located in the boiler (41), or in the high-temperature exhaust or drain pipe of other heat sources. The utility model is characterized in that: it further comprises a plurality of gas distribution devices (48) composed of a casing (49) and a rotary cylinder (76) therein, and the rotary cylinder (76) is fixedly connected to the outer casing (49). The central shaft (62) is provided with a small auxiliary cylinder (82) with a cold vent (85) and a large auxiliary cylinder (92) with a heat vent (93) arranged annularly around the central axis. The corresponding sized gas pistons (95, 85) in the large and auxiliary cylinders (92) and the small auxiliary cylinders (82) are connected to the swash plate (66) on the central shaft (62) via a connecting rod, and the rotating cylinder ( 76) The gear (77) on it is driven by the sun gear (27) on the main shaft (26); when the rotating cylinder (76) rotates, the cold vent (83) on the small sub-cylinder (82) can be respectively The air inlet (51) and the air outlet (53) provided on the small valve disc (50) on the side of the outer casing (49) communicate with the heat vent (93) on the large auxiliary cylinder (92). (49) The ventilation inlet (58) provided on the other large valve disc (56) communicates with the air outlet (60); the outlet passage of the compressor (8) (11) ) through the intercooler ( 14) and the inflator (51) on the small valve disc (50) of the gas distribution device, the ventilation outlet (53) of the small valve disc through the pipeline (55), the heater (36) And the insulated pipe (38) is connected to the gas exchange inlet (58) on the large valve disc, and the gas outlet (60) of the large valve disc is led to the gas inlet of the gas turbine (28) through the pressure insulated pipe (61). When the boiler is used as an external heat source, the intercooler (14) is disposed in an air cooling jacket (18) that exchanges heat in a countercurrent manner, and the cooling air outlet (21) of the cooling jacket passes through a pipe provided with a blower (24) ( 23) Access to the corresponding air inlet of the boiler (41).

2. The air turbine according to claim 1, wherein: in said gas distribution device, each of the large gas distribution pistons (95) in the rotary cylinder (76) is connected to the phase via the connecting beam (86) The corresponding small gas distribution piston (85) is integrally connected, and the inner side of the connecting beam has a concave portion (87) for avoiding the swash plate, and a sliding rail (88) is provided on the outer side surface of the connecting beam, in the rotating cylinder The inner side of the connecting shell (78) is provided with a seat rail (80) at a corresponding position, and between the seat rail and the sliding rail, a roller row (98) composed of a cage (100) and a roller (99) is installed; The cage (100) is provided with a plurality of double-row or intermediate-arranged single-row mounting shafts (102) arranged on both sides, and the shafts are provided with the same intermediate gears (101), and the gears and the seat rails The corresponding racks provided on the slide rails are engaged.

3. The air turbine according to claim 2, characterized in that: the gas distribution device (48) is arranged symmetrically or in a ring shape around the main shaft (26), and the air outlet (60) and the gas turbine (28) are arranged thereon. The air inlet is connected to the pressure insulated pipe (61).

4. An air turbine according to claim 3, characterized in that: a set of the same gas distribution device is arranged outside the symmetrical or annular arrangement of the gas distribution device (48), the gas distribution device and the inner side The gas device is installed at a certain angle, so that the corresponding air outlets (60) are respectively led to the air inlet of the gas turbine (28) through the elongated pressure insulated pipe passing through the gap of the inner gas distribution device, and the elongated spindle is extended. (26) The gear (77) on the rotating cylinder (76) in the air distribution device is driven by the outer center gear (27).

The air turbine according to claim 3 or 4, characterized in that the compressor (8) is arranged at the rear of the gas turbine (28), and the exhaust port of the gas turbine is arranged opposite to the inlet of the compressor, the two ports Connected through the communication channel (35), an air preheater (104) is arranged in the communication channel (35), and the exhaust port of the preheater is connected to the pipeline (108) provided with the blower (109). To the corresponding air inlet of the boiler (41).

6. An air turbine according to claim 5, characterized in that the air preheater (104) is provided by a number of heat absorbing flat tubes (112) which have a suitable length and The flow of the exhaust gas is arranged in the communication channel (35) of the ring-shaped table, and the heat-absorbing flat tubes are arranged radially in the annular communication channel, and the adjacent heat-absorbing flat tubes (112) are arranged by If thousands of heat absorbing sheets (113) are arranged in the direction of the air flow, the heat absorbing flat tubes are connected by the heat absorbing sheets to form a ring-shaped integral preheater structure, and the front end and the tail portion of each of the heat absorbing flat tubes are Streamline shape.

The air turbine according to claim 3 or 4, characterized in that the exhaust passage (34) of the gas turbine (28) leads to a corresponding air inlet of the boiler (41), and the exhaust passage is provided with ^ ( The bleed valve that opens when the power is turned on.

The air turbine according to claim 3 or 4, characterized in that the exhaust port of the gas turbine (28) is led to the outside through an exhaust passage (34) provided with an air preheater (104), and the air is preheated. The exhaust vent of the heat exchanger is led to the corresponding air inlet of the boiler (41) via a line (108) provided with a blower (109).

The air turbine according to claim 8, characterized in that: a bypass pipe with a combustion chamber (68) is provided at a periphery of the pressure heat insulating pipe (61) connected to the gas outlet (60) of the gas distribution device. Road (70) is provided between the inlet of the bypass line and the pressure insulated pipe (61) The swing valve (72), when the combustion chamber is burning, the swing valve (72) swings from the position of the closed bypass line to the pressure heat insulating tube.

10. The air turbine according to claim 8, wherein: the pressure heat insulating tube (61) connected to the gas outlet (60) of the gas distribution device is provided with an afterburner, and the telescopic fuel is provided. The injector extends into the afterburner when injecting fuel.