Turbine housing power system with gear housing
SUMMARY OF THE INVENTION 
     This invention uses less fuel to operate and pollutes less than conventional power plant systems. The power turbine system of this invention operates with two turbines that are in the same housing. The first power turbine produces the power and the second compressor turbine operates as a compressor system which absorbs the exhaust fluid from the first power turbine outlet and circulates and compresses the gaseous working fluid as it leaves the second compressor turbine outlet and flows to the condenser inlet. Both turbines are connected to each individual shaft and each of the individual gears in the gear housing system. The gear housing system is designed to allow the second compressor turbine to rotate faster than the first power turbine. The rotor of the second compressor turbine has more rotor blades than the rotor of the first power turbine. 
     If desired, the turbines in this invention, a first power turbine and a second compressor turbine that are in the same turbine housing, may be used in the turbine systems described in the Pat. Nos. 4,378,678 (Turbine System), 4,502,277 (Turbine Power Plant System), 4,420,941 (Cooling System), 4,733,537 (Turbine Power Plant with Exhaust Turbine Systems and patent application Ser. No. 07/150,636. The use of the second compressor turbine of this invention in conjunction with the turbines in the above mentioned patents may be of value in saving energy and producing less pollution than conventional power plant systems. 
    
    
     DESCRIPTION OF THE DRAWINGS 
     FIG. 1 is a schematic diagram showing the turbine housing which consists of two turbines located inside the same housing and connected to a gear housing. 
     FIG. 2 is a schematic diagram showing the interior of the turbine housing, the first power turbine, the second compressor turbine and the interior of the gear housing with a number of gears. 
     FIG. 3 is a schematic diagram showing the various gears and shafts in the gear housing. 
     FIG. 4 is a schematic diagram representing the turbine blades of the power turbine and the turbine blades of the compressor turbine. 
     FIG. 5 is a schematic diagram representing a closed loop turbine power system using the turbine housing in FIG. 1. 
     FIG. 6 is a schematic diagram showing a first passageway arrangement and a second passageway arrangement in a heat exchange relationship. 
     Before explaining the enclosed embodiment of the present invention in detail it is to be understood that the invention is not limited in its application to the detals of the particular arrangement shown since the invention is capable of other embodiments. Also, the terminology used herein is for the purpose of description and not limitation. 
    
    
     DETAILED DESCRIPTION 
     FIG. 1 represents the first power turbine 25 and the second compressor turbine 35 which are enclosed in the same turbine housing 20. The first power turbine 25 is connected to shaft 22. 
     Referring to FIG. 1, the first power turbine 25 receives the working fluid at point A and the exhaust fluid leaves the first power turbine 25 at point E. The second compressor turbine 35 receives the exhaust fluid of the first power turbine 25 at point E and the exahsut fluid of the second compressor turbine 35 is pressurized and leaves at point A75. Gear housing 27 contains different sized gears which allow the second compressor turbine 35 to rotate faster than the first power turbine 25. The rotor of the second compressor turbine 35 has more rotor blades than the rotor of the first power turbine 25. 
     The first power turbine 25 has a fluid conduit 75 which &#34;tapers in&#34; decreasing in size, from point A to point B at the inlet of turbine housing 20. The second compressor turbine 35 has a fluid conduit A75 which &#34;tapers out&#34; increasing in size from point C to point D at the outlet of turbine housing 20. The hot exhaust fluid leaves the first power turbine 25 at point E and enters the second compressor turbine 35 at point E at which time the working fluid is pressurized as it flows from point C to the outlet of fluid conduit A75 at point D. The cool condensed fluid from the condenser (not shown) enters fluid consuit A700 and absorbs heat energy from the hot exhaust fluid flowing from point D to point C, therefore preheating the working fluid coming from the condenser as it flows from the inlet of fluid conduit A700 to the outlet of fluid conduit 700 which then enters the heater (not shown). 
     FIG. 2 represents the interior operation of the first power turbine 13, the second compressor turbine 37 and their associated shafts and gears in the gear housing. The first power turbine 13 is operatively connected to gear 10 and shaft 75. The second compressor turbine 37 is operatively connected to gear 9 and shaft 17. Gears 15 and 12 are operatively connected to shafts 24 and 23, respectively. The bearing rings 21 and 22 support the main shaft 75, while bearing rings 19 and 20 support the second shaft 17 (shaft 18). Shaft 17 rotates outside the main shaft 75A (shaft 75). Shat 23 and shaft 24 are supported by support housing 28. Shaft 18 (shaft 17) rotates freely inside support housing 28 at point 6. Support housing 28 is split in half at point 29 for maintenance purposes, if needed. 
     Gear housing 28 contains a ring of bolts 27 which support gear 9 and the second compressor turbine 37, therefore not allowing movement between the two turbines, the first power turbine 13 and the second compressor turbine 37, at point 40. 
     FIG. 3 shows a crossection of the gear housing system, the first larger gear A2 is operatively connected to shaft A75 which in FIG. 2 represents gear 10 and shaft 75, respectively. The second gear in size is B4 which is operatively connected to shaft A17, which in FIG. 2 represents gear 9 and shaft 17, respectively. The two smallest gears D8 and A6 are operatively connected to shafts A23 and A24 which in FIG. 2 represent gears 12 and 15 and shafts 23 and 24, respectively. 
     FIG. 4 reprsents a schematic drawing of the rotor blades of the first power turbine and the second compressor turbine. Rotor blades C25 represent the blades of the first power turbine 25 in FIG. 1. Rotor blades C35 represent the rotor blades of the second compressor turbine 35 in FIG. 1. Conduit 75 in FIG. 4 shows the working field conduit which passes outside the rotor blades C25 &#34;tapering in&#34; (decreasing in size) from point A to point B at the inlet of the turbine housing. As the working fluid enters conduit 75, it hits all the rotor blades of the first power turbine continuously and equally. Fluid conduit 75 in FIG. 4 refers to fluid conduit 75 in FIG. 1. Fluid conduit A75 in FIG. 4 shows the fluid conduit which passes outside the rotor blades C35 &#34;tapering out&#34; (increasing in size) from point C to point D at the outlet of the turbine housing. The hot exhaust fluid of the first power turbine enters the second compressor turbine and is pressurized as it flows from point C to point D in fluid conduit A75 (which refers to conduit A75 in FIG. 1) 
     A low pressure area is created between the rotor blades C25 at the first power turbine outlet and the rotor blades C35 at the second compressor turbine inlet. This low pressure area is at point 40A in FIG. 4 and refers to point E in FIG. 1 and point 40 in FIG. 2. This low pressure area makes the sysem operate. The second compressor turbine has more rotor blades and rotates faster than the first power turbine therefore pressurizing the hot exhaust fluid coming from the outlet of the first power turbine rotor blades C25. 
     Cool condensed fluid enters conduit A700 and absorbs heat energy from the hot exhaust fluid coming from the outlet of the second compressor turbine. A heat exchange process occurs as the hot exhaust fluidf rom the second compressor turbine outlet flows from point C to point D at the outlet of the turbine housing giving its heat energy to the cool condensed fluid flowing in the opposite direction as it flows from fluid conduit A700 to fluid conduit 700. 
     FIG. 5 represents a schematic drawing of the flow of working fluid in the closed loop cycle of the power turbine system. The working fluid receives heat energy from an external source in heater 24. The working fluid flows from the outlet of heater 24 through point 2 to the inlet of the first power turgine at point 4. The working fluid enters and hits all the rotor blades of the first power turbine equally and continuously as it flows from point 4 to point 6. The hot exhaust fluid of the first power turbine enters the second compressor turbine at point 8 and is pressured out by the time it reaches point 10. The working fluid flows through the first passageway arrangements of fluid conduit 12 to the inlet of condenser 28 and then through the passageway of fluid conduit 33 to the second passageway arrangement of fluid conduit 14 at the outlet of condenser 28. The working fluid then flows through the second passageway arrangement of fluid conduits 16, 18, 20 and 22. A heat exchange process occurs in which the passageway arrangements of fluid conduit 16 through to fluid conduit 22 receives heat energy from the fluid flowing in the opposite direction in the first passageway arrangements of fluid conduit 12 through to fluid conduits 10 and 8, respectively, therefore preheating the fluid in fluid conduit 22. The working fluid then flows to the inlet of heater 24 at point 26 where it receives additional heat energy. 
     FIG. 6 represents two fluid conduits. The two fluid conduits are joined together to allow a heat exchange relationship between them. The passageway arrangements of the fluid conduits are separated and do not allow the fluid to mix together as shown by 30. The hot exhaust fluid flows through the first passageway arrangement entering at point 50 and leaving at pont 45. The first passageway arrangement is also referred to as the second fluid conduit means in the claims. The condensed fluid flows through the second passageway arrangement flowing in an opposite direction entering at point 39 and leaving at point 55. The second passageway arrangement is also referred to as the third fluid conduit means in the claims. In both first and second passageway arrangements a heat exchange relationship occurs between the two fluids. In FIG. 5, this heat exchange relationship starts at point 8 where the hot exhaust fluid from the compressor turbine flows through conduit 12 to the inlet of condenser 28. In FIG. 6 this refers to the fluid entering at point C and flowing through the conduit to point A. In FIG. 5, the cool condensed fluid begins its heat exchange relationship at point 16 and continues through conduit 22. In FIG. 6, this refers to the fluid entering at point B and flowing to point D. The condensed fluid from the outlet of condenser 28 absorbs the hot exhaust energy as it flows in an opposite direction, from fluid conduit 12 through to conduit 8 as shown in FIG. 5. A starter (not shown in the figures) is used to begin operation of the turbine housing power system.