Abstract:
A power plant incorporating attributes of a gas turbine engine, flywheel, and electrical generator (hereafter turbine/flywheel or TF) in a single compact unit, having a compressor arrayed with magnets which weight the periphery of the TF. Intermittent combustion periods accelerate the TF to a first rotational velocity, then combustion ceases, and the inlet/outlet of the TF are sealed, causing it to self-evacuate. Conductive coils surround the TF. Magnetic flux between the magnets and coils acts as a motor/generator, electrically powering a load, and absorbing electrical power therefrom via regenerative braking; power out decelerating the TF (now a flywheel), power in accelerating it. A pressure accumulator accepts the TF exhaust, and is pressurized by the combustion periods. Between combustion periods, exhaust in the accumulator expands in a small pump/motor that drives a generator, routing electricity to the TF to raise its rotational velocity.

Description:
RELATED APPLICATIONS 
       [0001]    This application claims priority of U.S. Provisional Application Ser. No. 61/457,755, filed May 27, 2011, entitled “Integral Gas turbine, Flywheel, Generator, and Method for Hybrid Operation Thereof”. 
     
    
     BACKGROUND SUMMARY 
       [0002]    Power plants typically produce peak power within a single proscribed operating range. This range is a design specification and invariably operation outside it is undesired. In instances requiring high power production, performance while underloaded is a secondary consideration and often the inefficiencies associated therewith are written off, as negligible in some instances such as wherein underloaded conditions are only encountered at the beginning and end of a long cycle. In some applications, the upper loading range can be an order of magnitude, or more, higher than the underloaded range. It is the inventor&#39;s understanding that the prior art is insufficient in offering a single power plant offering plural optimal operating ranges wherein the ranges are widely disparate in nature and wherein the power plant and the system comprised thereof are adequately small, lightweight, and simple. 
         [0003]    Hybrid systems have shown to be, thus far, the most efficient method of operating machinery, particularly vehicles. However, hybrid systems inherently incorporate multiple modules, each with its corresponding mass, volume, and complexity. Flywheels and batteries can be as massive as the prime movers they complement. In an effort to design purely complementary systems, the prime mover is constructed to be as small and light as possible, and the volumetric flow of combustion gases therethrough restricted to as little as possible, for reasons known to practitioners in the art. The maximum output is limited in such cases to the sum of energy stored and energy from the prime mover. Too often this is far insufficient, leaving industry with no non-hybrid choice but to waste considerable energy using a large engine to operate in the underloaded state, or fit a single piece of machinery with two prime movers. The hybrid solutions utilized to obviate these wasteful scenarios are complex and inordinately cumbersome. Although in certain applications theoretical optimizations of energy can be reached, the resulting masses and sizes of the resulting machines are simply out of consideration in many fields of endeavor. 
         [0004]    Specifically in dealing with high-power hybrid systems, a not uncommon example is the combination of an energy-storage mechanism with a turbine. Complexity and additional mass and size result from efforts to selectively engage one to the other, and both and/or one to the driven means. Also, considerable energy is wasted in the intermittent starting from standstill of the turbine. The most glaring drawback, however, is the fact that there are necessarily entailed three means; one for energy creation, one for energy storage, and one for energy transmission. In many uses this does not matter much, for the machinery that use the devices are slow, stationary, and/or off-road, such that size is not of issue, and, as mentioned, they are hybrid, such that energy put into acceleration of the superfluous mass is reclaimed during deceleration. However, there is still felt a need in the art for an equivalent system that is lighter, smaller, and faster. 
       SUMMARY OF THE INVENTION 
       [0005]    Disclosed is a power plant incorporating the attributes of a gas turbine engine, flywheel, and generator (hereafter “TF”) in an integral unit of remarkable compactness, obviating prior art solutions providing three disparate units, consequently reducing the overall weight and volume of hybrid systems. Also disclosed is machinery or a vehicle for use with the TF comprising a pressurized chamber, or pressure accumulator, and supplemental electrical and pressurized apparatus which cooperate to effect a method typically embodied by: 
         [0006]    a) a low-power, hybrid mode characterized by high efficiency; and 
         [0007]    b) a high-power mode characterized by high torque. 
         [0008]    Various (i.e. compressor, turbine) stages of the TF are arrayed with magnetized elements. The elements could represent a core of each rotor blade, being overlaid with a harder, sturdier material, or, if feasible, the blades themselves. Also envisioned are, in lieu of the foregoing or supplemental thereto, magnetized elements in other places, so long as those places are areas of high velocity near stationary (stator) locations capable of interacting with the elements. Coils are placed within said stationary locations and the electrons within them experience electromotive force due to the magnetic flux caused by passing magnets, creating energy. Conversely, movement of the electrons in the coils due to external electromotive forces causes physical acceleration and deceleration of the magnets. 
         [0009]    The utilization of the TF as a flywheel is thus inherent. Intermittent periods of combustion in the combustion chambers accelerate the TF to a first speed and then combustion ceases. The intake and exhaust paths of the TF are hermetically sealed. The TF, via means to be described later, continues to force air toward the combustor, whence it is withdrawn by a small pump, thereby effectively evacuating the TF and allowing it to spin with negligible drag. Electrical energy is drawn out of and into the rotating TF, decelerating it and accelerating it, respectively. Frequency and duration of the periods of combustion will be determined to disallow the rotational inertia of the TF falling below a level known to be minimal for power demands from consumers, and/or for unaided restart of the combustion process (in fact, due to the inherent method, a starter is obviated altogether). 
         [0010]    The exhaust passed downstream from the final turbine stage is accumulated in a pressure accumulator, preferably a large one representing the majority of the machine/vehicle not needed to support life. The exhausted air will be so lean (depleted) that it should surround the fuel tanks, motors, etc., such that the machine/vehicle and its constituent parts cannot of themselves combust. 
         [0011]    The accumulator will pressurize with exhaust until a certain pressure exists, at which point it is cut off from the TF via the latter&#39;s being hermetically sealed. The exhaust slowly expands (to environment) in a small reversible pump/motor or turbine which drives a shaft which turns a small, typical motor/generator. All pressures within the TF will atrophy to less than one atmosphere. 
         [0012]    Said small motor/generator, magnets/coils of the TF, motors (i.e. traction motors of a vehicle), and other conceived consumers communicate electricity, via respective transformers, inverters, converters, and so forth, along a DC bus. 
         [0013]    In a preferred embodiment, a novel gas turbine power plant is used to complement the nature of the hybrid operation, and consists of an everted flow-path with the turbine stages disposed radially inwardly of the compressor stages. The first compressor stage and second turbine stage are of the centrifugal type, providing the highest possible head over the shortest axial length, and effecting narrow, combined, concentrically paired ducts for the intake and exhaust. In other words, the TF exhausts and intakes from the same end, the exhaust and intake are parallel and concentric, and the combustion is at the other end. By careful placement of all intervening items, the entire system should be capable of fabrication to dimensions not in excess of 2.5 feet in any direction, enabling its placement within a passenger vehicle or other environment where size is restricted. Also, proper material selection should result in a mass not much higher than a typical hybrid vehicle. However, larger, more or less massive versions could be utilized in heavy machinery, large vehicles, water- and air-craft, etc. 
         [0014]    One thing should be pointed out concerning the novel power plant geometry. All stages are arranged to, when the main unit is sealed off, force air toward the combustor. With proper placement of bypass valves—specifically inter-stage seals that automatically leak when a pressure-drop across them falls below a threshold—the power-plant, not only efficient in its use of space, evacuates itself much more quickly from a single bleed point (preferably in the combustor) than traditional (linear axial) systems ever could, further reducing the number of moving parts. Again, the TF charges an accumulator, the pressure in the accumulator drives a pump, the pump, TF, and utility motors direct electrical energy away from and toward each other along a DC bus. A heat exchanger directs the initial intake air past the air traveling from the last turbine stage to the accumulator. Further, a recuperator can be advantageously positioned to heat the combustor inlet with a turbine outlet. The recuperator, the heat exchanger, and supplemental heat exchanges inside the accumulator, such as the heating of fuel, should sufficiently cool the exhaust air so that it does not harm the chamber, which is desired since the materials best suited for the accumulator due to their tensile-strength-to-weight ratios decompose at high temperatures. 
         [0015]    During sustained high power output all available power is directed to the compressor/turbine module attached to a main drive shaft. In the preferred embodiment, the first turbine stage produces work whose sum is delivered to said shaft after having the work of the axial compressor stages subtracted therefrom. Also, in the preferred embodiment, the second turbine group, of the centrifugal type, drives the first compressor, also of the centrifugal type. This stage has also associated therewith its own corresponding magnets and coils, and as it rotates freely, in a preferred embodiment, of the main module, its power will be fed in the form of electricity to the magnets of the main module, and thereby, to said main shaft. Additionally, the downstream, post-chamber reversible pump/motor or turbine, will no longer expand the accumulated exhaust slowly, but will be run up to a maximum speed, while the transformer associated with its corresponding electrical generator, of the variable type, will have its ratio changed (as would a mechanical transmission, its ratio should always be varied to allow the generator, when the generator drives the TF, an electro-mechanical advantage; likely this could be effected by constantly varying the number of coils connected in series on the toroid) to match the now rapidly turning and highly torqued shaft associated with the generator. In this way the constant stream of exhaust into the chamber can be dealt with and its high pressure utilized for optimal power production. The pump/motor can also be wastegated by another system within the machine. Consequently, this considerable electrical power produced by the reversible pump/motor or turbine will be fed, via the generator and transformer, to said magnetized vanes of the main (axial) compressor, the confluence of it with said EMF from the turbo-charging stage will further torque the main shaft, complementing the physical torque from the first turbine stage, such that, although the turbines and other producers of energy are spread about the overall system, the shaft transmits, selectively or not, all available power to the high-output consumer. 
         [0016]    An electrical control system will selectively connect (as well as convert, invert, and/or transform, as needed) each driven and drivable element with the DC bus, via prior-art means. An AC bus is not unforeseen, however due to the inflexibility associated with its embodiment, it would disallow the independence of all the systems, and would therefore be difficult to realize in a dynamic system, without extensive control provisions. For static systems, with masses, volumes, geometries, and electrical components matched for a predetermined energy production, alternating current could be preferred. 
         [0017]    However, the advantage of the DC bus is that it obviates transmissions and clutches, and any shafts, axles, gears, levers, housings, collars, and cooling and lubricating systems associated therewith. A control system will actuate small switches and corresponding governors of current, such that the consumers and producers always operate at the most efficient, or demanded, speed and torque. For the TF during flywheel stage, this speed is much higher than is achievable by the fluid reaction on the turbine vanes. The traction motors can decelerate the vehicle (if it is a vehicle the system is being used in) or accelerate it, regardless of speed of the vehicle, and the TF can always be accelerated, despite the fact that it might already be rotating very quickly, as the torque on the main compressor/turbine group will always be proportional to voltage applied, since the incoming electrical energy will always be oscillated with a frequency, and timing, perfectly attuned. The methods for doing this are well known in the electrical arts. 
         [0018]    Thus, pursuant to the forgoing, the reversible pump/motor or post-chamber turbine can be embodied by just about any combination of expanders. It is known, particularly from steam turbine and other stationary power-plant application, that the higher the number of turbines and heat exchangers, the better; in other words, the asymptudinal theoretical limit on efficiency can only be approached via a nearly infinite array of turbines and heat exchangers/engines. The enthalpy escaping the combustor requires near-infinite successive mechanisms to extract all kinetic and heat energies, or finite mechanisms and infinite time. Clearly there is a trade-off involved in the field of endeavor of the instant application, weight and volume vs. un-extracted enthalpy. Infinite time is the key to comprehending the initiative of the invention. 
         [0019]    Since the instant invention provides for cooling between the exhaust from the TF and the post-chamber expander(s), the material requirements for the latter are eased; not only via the parallel-flow heat exchanger envisioned and described below, but also via a recuperator that is inherent in the geometry of the TF&#39;s preferred embodiment, and some residual heat losses. The enthalpy of the exhaust, at the point it arrives to the reversible pump/motor or post-chamber turbine, is disproportionately represented by kinetic (pressure) energy, the heat energy having been mitigated to acceptable levels and no longer deleterious to downstream matter (but if not, additional heat exchangers could be utilized, or even a heat pump, the energy of the latter routed the way, via electricity, of all the other energies of the system, for the temperature of the post-chamber air will only be a problem during high-output, non-intermittent operation). The disproportionately kinetic nature of the enthalpy can be nonetheless rendered, and to what extent it can be rendered is the subject of Appendix I. 
         [0020]    Any of α-aj from Appendix I can be used to drive either along a single shaft or other mechanical means a single generator or multiple generators, or via multiple shafts or other mechanical means a single generator or multiple generators. Additionally, the generator or generators aforementioned can receive power from the DC bus to drive, either in reverse or through a reversing assemblage of valves or variable vanes, said one or a combination of items a-aj, to charge the chamber. The simplest embodiments of a-g will be dealt with in the description of the preferred embodiments, and their foreseen combinations as per h-aj should be seen as serial, or parallel, co-utilizations not incomprehensible, unimaginable, or unobvious to one of ordinary skill in the art, once put forth as has been done in Appendix I. 
         [0021]    In a preferred embodiment, one or more of a-aj is attached to a shaft shared by a clutch/transmission arrangement to provide, on demand, regenerative braking wherein the slowing of the shaft charges the chamber, with or without simultaneous electrical generation by the generator(s). In said preferred embodiment, a service (mechanical) brake is also provided along the shaft to act, upon actuation by a clutch or equivalent means, whenever the combined load of the generator and reversible pump/motor(s) and/or turbine(s) is insufficient to brake the vehicle, as well as when the vehicle has regeneratively been braked to a full stop. In the event that the reversible pump/motor(s) and/or turbine(s) and/or generator(s) are used to decelerate a vehicle, it is foreseen that prior art anti-lock braking algorithms will be used to selectively connect the loads of them, as well as the load of the emergency-brake, to the axle. 
         [0022]    Where, in such applications as single-engine aircraft, Coriolis forces must be mitigated to every feasible extent, the turbo-charging stage (compressor group  1 ) rotates in a direction counter to that of the axial-compressor (compressor group  2 ) and first turbine stage (turbine group  1 ). As this increases the demand on any bearings between them, in any application where Coriolis is not of issue, the direction of rotation of all stages in the main TF unit should be identical. However, in any event, the most efficient arrangement, and thereby best mode, although its opposite is not un-considered by any means, involves the turbo-charging stage (even if it comprises axial compressor and axial turbine, even if it these are not concentric, even if it comprises axial compressor and centrifugal turbine or vice versa, even if all are concentric or they are separated greatly by space or not adjacent) and main unit rotatable relative to one another, since (as is the case of concentric dual- and triple-shafts of typical gas turbines) each will desire its own rotation rate to maximize efficiency. The capability of relative rotation is also necessitated by a “virtual clutching” method for engagement of the high-consumer, described below. 
         [0023]    Also considered is the possibility that variable rotor vanes could be utilized in lieu of the self-evacuation. For instance, the vanes of the compressors could be completely closed via cascade rings or equivalent structure, such that the lead edge of one abuts the trail edge of another. This, too, would reduce internal drag on the TF to close to negligible. However, it is likely this system would be inordinately complex, and embodied likewise would detract from the robustness and compactness of the system. The speeds at which the TF will experience, and the shocks on it during the sealing and unsealing of the flow path, require as few moving parts (seen in the relative frame of the TF) as possible. As a side note, one of the advantages of the first compressor and last turbine stages&#39; being of the centrifugal variety is to absorb the shock of said sealing off the flow path. It is doubtful axial-flow vanes, being cantilevered (perhaps even if ringed around their periphery with a runner, which is also envisioned anyway), could withstand the pressure fluctuations experienced along the first few axial inches of the compression system, without a buffer in the form of vanes of the type of a centrifugal compressor, to protect them. However, an additional buffer is provided in the preferred embodiment, in the form of the thin walls of an upstream heat exchanger and manfold, which by being of the plate-type and if thinly walled enough will bellow momentarily inwardly at the commencement of evacuation, such that the combination of the variable volume walls of the heat exchanger between the main inlet and the first compressor inlet, and the means, that by which the first two to four atmospheres of head are accrued (i.e. a centrifugal compressor and turbine nearer the seal-off point than intermediary members), being unbreakable, should ensure the compressor rotor vanes do not break, which is crucial since any alloying of the ferritic, neodymium, etc. cores will possibly diminish magnetizability, assuming blade-magnets are utilized. 
         [0024]    As there is a DC bus, so also must the pressure accumulator be seen as a “pressure bus.” It is an accumulator, and thus all accumulations thereto and expenditures therefrom, however independent in their utilization, augment or deplete, respectively, the stored pressure energy. For this reason it is not surprising that there are further uses with which it can be associated. 
         [0025]    For instance, the shock absorbers, in the event that the machinery is a vehicle, can feed the main chamber via means known by prior US patents. Particularly in the embodiment of an automobile, a simple leading arm with a chain- or belt driven wheel receiving motive power from a motor along the arm, while up and down perturbations experience due to contours in the road cause movement against a piston and spring, heightens the hybrid aspects of the foreseen embodiments. Following the teachings of said patents, the initial deflection of the rod will charge the chamber, as will the reaction by the spring to home the rod. The chamber, being ubiquitous, is ready and willing to assume this energy for future use, and the acceleration it later provides will almost negate the deceleration caused by the contour. It is expected that this provision will more than make up for the added cost and weight associated with replacing a typical shock absorber with one of said patents, however they were disused in their own time. 
         [0000]    Mode-Change: from Hybrid Operation to High-Consumer Operation 
         [0026]    In a preferred embodiment no clutch is required for connecting the main shaft (MS) to the high-consumer drive. When engagement of the high-consumer is desired, the primary TF module (PTFM) is braked electrically, all its energy (the TF system inlet and outlet being closed, combustion ceased, the TF system evacuated) being transferred electrically along the electrical bus (EB) to the secondary TF module secondary turbine/flywheel module, accelerating it. The pressure accumulator PA is depleted of any contents rapidly through the pump/motor (PM 1 ), the electrical energy obtained therefrom also being transferred to the secondary turbine/flywheel module along the DC bus. The secondary turbine/flywheel module now comprises more or less all the stored energy of the overall machine in the form of rotational kinetic (inertial) energy. 
         [0027]    When the main shaft MS and high-consumer drive shaft have equivalent rotational velocities (not necessarily zero, as discussed later), a sleeve or collar associated with a differential (or similar torque transfer mechanism) associated with the drive shaft will be forced in a longitudinal direction (relative to the main shaft), to mate with a protrusion structure on the main shaft In some applications a slot or groove, or a plurality of either, will embrace a trunnion or like, or a plurality thereof, on the main shaft. In other applications, the main shaft will be splined on its outer diameter, and the sleeve/collar machined on its inner diameter to interfit, or vice versa. Other embodiments are foreseen. Countless arrangements are known to those of ordinary skill in the art for engaging a shaft to torque transfer means when their speeds are matched during engagement, and the simplest is of course preferred. The selection of one or the other is not of issue in the instant application. A clutch might be used, with or without the provision of matching the speeds of the shafts, as could any other means known in the art. All that is of essence in this discussion is that in a preferred embodiment the clutching is “virtual.” Actual slip between the two shafts would be detrimental, but what is most detrimental is a dissipative effect on the spinning components. Most advantageously, a simple collar that does not even touch the shaft until engaging it precludes viscosity or frictional resistances to free- or fly-wheeling desired during hybrid operation. The obviation of the clutch by the virtual-clutch method is fundamental to realizing the theoretical efficiency of the proposed invention. An added benefit is that surplus energy from hybrid mode is transferred directly into the high-consumer mode. 
         [0028]    Continuing, once the main shaft and torque-transfer leading to the drive shaft are matched in speed at their engagement point, they are positively locked for rotation together. Subsequently, the primary TF module and secondary TF module are electrically connected one to the other and allowed to approach equilibrium via the transfer of energy from the secondary turbine/flywheel module to the primary turbine/flywheel module along the electrical bus. When optimal speeds have been reached for both, combustion commences. The torque generated by the secondary turbine/flywheel module, the latter comprising no drive shaft in the preferred embodiment, continues to transfer to the primary turbine/flywheel module (and thereby to the main shaft) along the DC bus. Likewise for the pump/motor PM 1 , which should be operated in a manner and at a capacity to optimize the available pressure within the pressure accumulator (PA 1 ), now being continuously charged by the TF system. 
         [0029]    In other words, the power available from turbine group  2  is transferred, minus the load required by compressor group  1 , via the magnet/coil arrangement, to the DC bus. Meanwhile, the power generated by the pump/motor PM 1  (now operating as a motor) is transferred, via its corresponding motor/generator MG 1  (now operating as a generator), to the DC bus. The magnet/coil arrangement on the primary turbine/flywheel module consumes all the power from the DC bus, torquing the primary turbine/flywheel module in its drive direction. The amount of power available from the DC bus is subtracted from the load requirement on the main shaft (from the drive shaft), while the load on compressor stage 2 is added thereto, and the resulting power demand is provided by controlling the combustor to impinge combustion gases upon the rotor vanes of turbine stage 1. 
         [0030]    The following equation appertains: 
         [0000]        P   required of turbine group 1   =P   drive shaft   +P   compressor group 1   +P   compressor group 2   −P   turbine group 2   −P   PM1   [Equation 1]
 
         [0031]    Optimization of each module, geometrical and operational, can be determined by an iterative approach for each industrial application, for the contribution of P PM1  will be a function of the capacity of the PA, while P compressor group 1  and P compressor group 2  will be a function of the desired size of the TF system, P drive shaft  will be defined by output specifications, etc. 
         [0032]    The foregoing distinguishes the high-consumer mode from the hybrid mode, and sets it aside in a view toward design. During hybrid operation, the primary turbine/flywheel module and secondary turbine/flywheel module accelerate and decelerate independently unless one falls to a speed threatening to stall future combustion attempts or fail on an impending increased required EMF to the bus, at which point a quick equilibriation between the two may be initiated. All systems communicate with the bus unconcerned with one another, unless the system controller predicts a future problem (e.g. insufficient inertial energy of TF system relative to pressure within the pressure accumulator, in which case the PM 1  would increase its capacity, such that PM 1  can always, unless commanded otherwise, operate at the slowest possible (and therefore most efficient) rate. The load, also, should be operated solely upon input and output considerations at the load itself. 
         [0033]    The independence of all of the units in the hybrid mode allows Equation 1 to be solved for the high-consumer mode first. The result of an iterative operation to determine the make-up of the units to satisfy the high-consumer will, it is hoped, produce a system just as efficient in hybrid operation as any other (standard HEV) would be, especially considering the ratios P turbine group 2 /P compressor group 1  and P turbine group 1 /P compressor group 2  will follow roughly the same curve, vs. throughput, as each other. Discrepancies between the energy available in primary turbine/flywheel module and secondary turbine/flywheel module can always be adjusted by equilibrating them, presuming they do not inherently automatically equilibrate, which they probably will. It is perceived, however, that the specifications of PM 1  in hybrid mode will likely take precedence over said of high-consumer mode. In any case, solving for both simultaneously is not beyond currently marketed simulation software. 
         [0034]    Solution of Equation 1, and considerations springing therefrom, will be the subject of further research as well as, in the event the results are surprising or entail further structural or operational advancements, the subject of continuation-in-part applications, whereupon no rights are waived and, following this string, considering the system as construed for an automobile would be monstrously different, schematically (on paper), quantifiably (sizing), and qualitatively (material selection), from that of, say, an earth-mover, it is here asserted that, barring truly innovative improvements, these results will be no more than an extrapolation of the novel concepts, as well as the novel assemblage of concepts, put forth in the present application, and therefore obvious to one of ordinary skill in the art. 
         [0035]    In any and all areas of application, it is anticipated that all parts should be as light, yet sturdy, as possible, all magnets and conductors as effective as possible, etc., limited only by cost-benefit analysis. If it is decided to run the system on fuel-A, all pre-treatment and exhaust features associated with fuel-A will no doubt be modifications to the present invention suggested by art dealing with fuel-A in other applications. Similarly for fuel-B, etc. The shape and size of the combustors can be selected from any that can be shaped and mounted to complement the system and conform to the geometrical constraints posed by the chosen industrial application. Prior art suggesting modification for respective optimization of various seals, vanes, bearings, circuitry, ducting, shafts, airfoils, fans, motors, generators, pumps, etc. of other known systems are inherently and necessarily suggestive of modifying the seals, vanes, bearings, circuitry, ducting, shafts, air foils, fans, motors, generators, pumps, etc., of the present invention. 
       Mode-Change: Back to Hybrid Operation 
       [0036]    Switching from high-consumer mode back to hybrid mode does not have to be a mirror image of the switch from hybrid mode to high-consumer mode, although it could be. In fact, the preferred manner of achieving said switch is an abrupt decoupling of the collar/sleeve from the MS. Only in special applications would there exist the possibility of recapturing the energy already passed on to the high-consumer. Thus, if the mating action that effected the coupling were reversed without matching the main shaft speed to that of the torque-transfer leading to the drive shaft, the TF system would already be well on its way to its post-run-up speed, and the drive shaft would run itself down with negligible rotational inertia excepting that of whatever load it heretofore had driven. It is foreseen that this will not always be preferred, in which case the “mirror image” might be viable or, if wasteful of time or energy, something between one and the other of the two methods described in this paragraph. As in prior discussions, the end-use will dictate the means, although the best mode is believed by the inventor to have been adequately disclosed, particularly as the “preferred” manner corresponds to the example utilized hereinbelow to discuss the manifestation of the system in exemplary industrial applications. In no way should the examples be limiting. 
       INDUSTRIAL APPLICABILITY: AN EXAMPLE 
       [0037]    It will be obvious to one of ordinary skill in the art that a surplus energy due to stored pressure is constantly available during high-output mode. Each application will find its use for this energy, but nowhere is it more to be availed than in the application of a roadable aircraft. In fact, such an automobile is an excellent example of the potential industrial applicability of the invention. 
         [0038]    Thus, a vehicle is disclosed, having an effective cross-section of a modified airfoil. Customs of usage require that the vehicle be inconspicuous, in appearance akin to known automobiles. However, it is proposed, that the power-plant and associated system, housed and modified appropriately, enable a wheeled vehicle similar in appearance to a typical streetcar, to operate as an airplane, capable of takeoff from and landing on road, driveway, heliopad, roof, lawn, and still water. These attributes are derivative fruits of the innate arrangement of the system heretofore described. The inventor has extrapolated from said fruits to purport at least a working, if not perfected, embodiment for realization of such a vessel. 
         [0039]    The embodiment&#39;s common name is a roadable aircraft. Like in other prior art pursuits, the effective cross-section of the majority of the width is made to encompass all the working modules of the system. Said effective cross-section, that of a modified airfoil, can be destroyed by flaps, louvers, fins, etc., such that, until lift is desired it is nonexistent or negligible. Further desired are the parts not associated with the effective cross-section, those that render the appearance of the vehicle to be not overtly dissimilar to a standard car, and those which convene daily use by a driver. However, the advantages of the concept herein disclosed cannot be overlooked. With a glance at the provided figures, although they should not be seen as limiting, it is clear that the airfoil can be realized, following the methods hereafter detailed, such that once it is provided, given a certain thrust lift is inherent. Thrust is provided in the preferred embodiment, in the form of an impeller/fan/propeller/etc., rotated within its housing, or with no housing, by the drive shaft, via or not via intervening gears, clutches, etc. from the TF main shaft. Two of the three underlying predicates of sustained flight have been here met, for it follows (from Bernoulli&#39;s principle] that given sufficient speed, the airfoil-cross-section will provide adequate lift, and that given the weight and throughput of the disclosed power plant, adequate thrust has been provided to attain said speed. It is a foregone conclusion, since the advent of, say for instance, nozzle-directed air-to-air missiles, that an accelerometer combined with a respectable computer processor, and in the event these are insufficient some marginal attempts at ailerons, hereafter discussed, can use “offset nozzles” to reduce all pitch/roll/yaw stabilization concerns to nil, producing a steady craft if there were a way to embed pressurized cartridges with nozzles on the four corners of the craft—so, serendipitously for us, the entire housing PA 1  is a pressure cartridge. What is hereinafter proposed is that nozzles, each in communication with the chamber across a controlled valve, are located at the very front of the vehicle, on each front corner one pointed up one pointed down, and one pointed laterally outward, totaling six, so as to in reaction to an accelerometer and “desired course” models, pre-programmed yet modifiable, enable a computer processor to stabilize the vehicle. It is conceded that this procedure will be involved, but not beyond ordinary skill in the art, for if a missile can be made to hit another, nozzles can surely be set to maintain the sustained flight of an airfoil of considerable MOI about all axes, given thrust and lift requirements have been met. 
         [0040]    The following provisions are envisioned: 
         [0041]    a) a vertical take-off “VTO” nozzle placed on the nether extent of the vehicle, to provide downward exhaust impingement of the pre-expanded chamber air on a vertically inferior portion of road or air, selectively augmenting lift; 
         [0042]    b) a vertical take-off “VTO” panel set in the rear of the vehicle, to complete or destroy air-foil cross-section in a longitudinal sense, augmenting lift in the airfoil sense while hiding, closing, and protecting, in the airfoil-destroying sense, the impeller. The VTO panel comprises minor panels, controllably actuated along a spectrum of opennesses, for deflection of thrust from the impeller downwardly. 
         [0043]    The geometries of the power plant, electrical apparatus, motors, and vehicle shown in the figures, should not be seen as limiting, but as the best mode envisioned at the moment by the inventor in its simplest embodiment. No doubt considerable computer modeling will alter the final shape of each item depicted in the drawings, as will subsequent improvements, made either by the inventor or by the industry. The essence of the invention is in the novel combination of heretofore uncombined technologies and parts, as set forth in the claims appended hereto. 
         [0044]    In the same vein, it is proposed here with profound emphasis that the roadable aircraft is a secondary consideration of the instant application, the claimed subject matter dealing primarily with the hybrid motor and the industrial applicability of said, and the inventor reserves the right to follow with, a propos of discernible industry demand, continuation, divisional, and continuation-in-part applications concerning the inner workings of the system of the power plant or its workability, the mechanical and/or electrical interrelationships of the terrestrial applicability of the machinery, or the aerodynamics of the vehicle as so far conceived, as befits his interest, none of the matter not within the scope of the claims hindering or compounding the U.S.C. sections 101, 112, 102, and 103 requisites beyond any reasonable objection by the PTO, insofar as the gist of the claimed subject matter has here, or in subsequent paragraphs, been delineated ad nauseum. Whether the TF in effect pertains to one high-user or another and to one low-user or another (high and low corresponding to the two stages of the invention, the first low-power, hybrid output, and the second high-power, non-hybrid or quasi-hybrid output, respectively), the scope of the instant application should not be seen as limiting save insofar as the appended claims delegate. 
         [0045]    Since flywheels require high peripheral weight, since generators require magnets and coils, and since turbine engines require high peripheral speeds, the invention kills all three birds with one stone. Another system using weighted element(s) for the flywheel, separate magnets for the generator, and some non-negligible mass for the rotor blades, is necessarily more massive and voluminous than the instant invention. 
         [0046]    The field of endeavor of the instant application is vast, and the examples used to depict advantageous manifestations of the inventive concept should by no means be limiting. For instance, the low-power/high-power combinability applies to, mentioning only a few: earth-movers and other dump trucks, tow trucks, tugboats, tankers, fifth-wheel-hitch-enabled cabs (tractor-trailers), etc., wherein the electrical energy and shaft torque would be directed to a single consumer or set of consumers, through gearing or appropriate circuitry delivered along a single shaft or multiple shafts. For instance, the drive shaft of an idyllic tugboat or tow vehicle would be favorably received by the industry in conjuring 7-10X horsepower from an engine that can run at maximum efficiency at 1-2X, X being a coefficient. Equivalently for unladen earth-movers and tractor trailers or for tow vehicles for earth-movers or tractor trailers. Also propitious seems some form of “universal tool”, wherein the vehicle would be a portable PTO (power take-off) shaft connectable to a fleet of unpowered implements. Not among the least likeliest embodiments is the arrangement of the power-plant and chamber proffered as a possible solution to fixed-wing VTO pursuits. It is not foreseen that the invention will be immediately advantageous in typical applications such as terrestrial passenger vehicles, trains, etc. The advantages will, possibly, only make up for the increased material costs by providing, on demand, a non-hybrid mode of high power output capabilities. 
         [0047]    One end of the main shaft of the TF is selectively engaged to a high consumer, such as the propeller/fan of an aircraft, a work implement, hydraulic pump, etc. In fact, with proper arrangement and in conjunction with proper body geometries, described in this document, the hybrid system can be utilized in a roadable aircraft. However, it is also foreseen that, with time and given a great deal of perfection, not to mention mass-production, the unit could be viewed as applicable to environs not requiring the high power mode, such as in metro-buses. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0048]    The foregoing discussion will be understood more readily from the following detailed description of the invention, when taken in conjunction with the accompanying drawings. 
           [0049]      FIG. 1  is a flow diagram for the flow of gases through the various modules used to implement the present invention. 
           [0050]      FIG. 2  is a semi-cross-section (cross section of one sector) of the turbine flywheel TF showing the compressor, turbine, stator, generator, and combustion modules. 
           [0051]      FIG. 3  illustrates an embodiment of the reversible pump-motor PM 1 , the motor-generator MG, and the transmission between these and the drive axle of a vehicle. 
           [0052]      FIG. 4  is a gas flow strategy for selectively changing the mode of expansion through the reversible pump motor. 
           [0053]      FIG. 5  is a table explaining the six currently foreseen combinations of valve settings for  FIG. 4 . 
           [0054]      FIG. 6  is a cross-section taken along line  6 - 6  of  FIG. 9 , showing the effective cross-section of the majority of the vehicle of the first embodiment of the invention. 
           [0055]      FIG. 7  is a cross-section taken along line  7 - 7  of  FIG. 9 , showing the cross-section at the center of the vehicle of the first embodiment of the invention. 
           [0056]      FIG. 8  is a cross-section taken along line  8 - 8  of  FIG. 9 , showing the cross-section at the side of the vehicle of the first embodiment of the invention. 
           [0057]      FIG. 9  is a top cross-sectional view of the vehicle of the first embodiment of the invention, providing basis for  FIGS. 6-8 . 
           [0058]      FIG. 10  is a rear elevational view of the vehicle of the first embodiment of the invention. 
           [0059]      FIG. 11  is a table providing the chronology of steps utilized in hybrid operation of the first embodiment. 
           [0060]      FIG. 12  is a table providing the chronology of steps utilized in transitioning to high-consumer mode from hybrid mode, and also for transitioning back to hybrid mode, or a parked configuration, from the high-consumer mode. 
           [0061]      FIG. 13  is a continuation of  FIG. 12 . 
           [0062]      FIG. 14  is a view of a rotor vane of the axial compressor shown in  FIG. 2 . 
           [0063]      FIG. 15  is a cross-section taken along line  15 - 15  of  FIG. 14 , showing the magnetic core of the rotor vane of the axial compressor. 
           [0064]      FIG. 16  is a close-up of area A of  FIG. 2  showing the bias seals of the turbine flywheel module. 
           [0065]      FIG. 17  is a top or bottom view of a VTOL aircraft of a second embodiment of the invention. 
           [0066]      FIG. 18  is a cross-section taken along line  18 - 18  of  FIG. 19 , showing the in-wing orientation of the parts in the second embodiment of the invention. 
           [0067]      FIG. 19  is an elevational view from above the wing of the aircraft of the second embodiment of the invention, showing the fan, wing, ailerons, and VTO flaps of the second embodiment of the invention. 
           [0068]      FIG. 20  is a view of the casing of the turbine flywheel and the gas transmission passage of the second embodiment. 
           [0069]      FIG. 21  is a top cross-section of the combustor of the turbine flywheel. 
           [0070]      FIG. 22  is a bottom view of the turbine flywheel showing the spacing of the combustors around the turbine flywheel. 
           [0071]      FIG. 23  is a schematic of the gas flow for a first mode of operation of the second embodiment. 
           [0072]      FIG. 24  is a schematic of the gas flow for a second mode of operation of the second embodiment. 
           [0073]      FIG. 25  is a schematic of the gas flow for a third mode of operation of the second embodiment. 
           [0074]      FIG. 26  is a side view of s vehicle utilized in implementing a third embodiment of the invention. 
           [0075]      FIG. 27  is a rear elevational view of the vehicle utilized in implementing a third embodiment of the invention. 
           [0076]      FIG. 28  is a side view of the vehicle utilized in implementing a third embodiment of the invention towing another vehicle. 
       
    
    
     DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS 
       [0077]    The following description of  FIG. 1  is meant to be understood in conjunction with  FIG. 2 . The flow chart of  FIG. 1  shows the flow of gases through the entire system. Air enters the system from air intake  1  and passes, via a shutter valve (described later) after traversing a heat exchanger (described later) to the first compressor group  2 . The air is compressed by first compressor group  2 , which is driven by the second turbine group  5  and is integral with the first generator/flywheel  6 . The air passes from the first compressor group  2  to the second compressor group  3 , which is driven by the first turbine group  1  and is integral with the second generator/flywheel  7 . In the embodiments of the present application,  2 ,  5 , and  6  are concentrically arranged about a longitudinal axis  50 , and  4 ,  3 , and  7  are also concentrically arranged about said longitudinal axis  50 . After the second compressor group  3 , the compressed air enters a combustor C, which for this discussion can be seen as a typical combustor can but which will later in the application be discussed further a propos of its geometry when applied to the TF. The exhaust from the combustor passes to the first turbine group  4  and then, after traversing a recuperator R, to the second turbine group  5 . The exhaust passing from the second turbine group enters, via a shutter valve (described later), a pressure accumulator PA 1 . 
         [0078]    The pressure accumulator can be large and in the embodiments of the present application it surrounds the greater part of the TF casing and is confined by the outer walls of a vehicle. The pressure accumulator PA 1  communicates with the ambient air outside of the vehicle via a reversible pump/motor PM 1  and possibly other pump/motors  12 , which when driven by air expanding therethrough are motors, usually driving a motor/generator (in the case of PM 1 , it drives MG 1 ), and when taking air into the pressure accumulator PA 1  to charge it to higher pressures, are driven by the motor/generator and act as pumps. Further escape valves allow gases within the pressure accumulator to pass directly to the environment, as shown by passageways a, b, and c leading from the pressure accumulator PA 1  to outside  13 . Shaft  11  depicts the rotational interlock between the reversible pump/motor PM 1  and the motor/generator. Motor/generator MG 1  is electrically connected to a DC bus  15 , which communicates with first and second generator/flywheels  6  and  7 . The DC bus is further connected to the load L, which could be in-wheel electric motors with regenerative breaking reversing the electrical flow back to the bus from the load. The DC bus is also connected to auxiliary systems, the cabin, and possibly (in embodiments not of interest in the present application) a battery and/or docking station. An evacuation pump  8  is connected to the combustor C, preferably near the air inlets or near the burner nozzle, possibly in conjunction with the latter, and when activated causes a negative pressure which removes any air in the combustor. This will be described later. 
         [0079]    The air from the evacuation pump also passes out to ambient  9 . Reference numeral  10  indicates a further provision, not dealt with in the present application, whereby instead of expanding the gases through PM 1 , or in addition thereto, the gases in the accumulator are passed through the first and second turbine groups  4 ,  5 , again, without combustion, to ambient. This provision is not at this time seen as fruitful, but has been included for the sake of full disclosure. 
         [0080]    Turning now fully to  FIG. 2 , although reference may be made to  FIG. 1  throughout the disclosure, the air entering the inlet  20  is shown as airstream  22 . After the inlet  20  it enters a centrifugal compressor C 1 , which in this embodiment makes up the entirety of the first compressor group  2 . The air passes outwardly along compressor C 1 , being thereby pressurized and flung into volute V 1 , where it may be guided by diffuser D 1  and/or stator vanes, swirl vanes, anti-swirl vanes, etc. into the first stage (C 2  and S 1 ) of the second compressor group  7 . The compressor C 1  is attached to, and locked for rotation with the second turbine group  5 , namely the fourth turbine stage T 4  which is a centrifugal turbine. The compressor itself is, and in this case the vanes between the air passages are, embedded with magnetic elements M near the casing  21  and preferably as far to the radially outer extreme of the compressor as possible. The magnetic elements interact with conductive coils i in or on the casing to create or absorb electrical current. The magnetic elements M plus the conductive coils i make up the first flywheel/generator  6 , in that the mass of the magnets plus the combined masses of the compressor and turbine carry a rotational inertia about 50 which resists the voltage acting against its continued rotation during electrical current creation. Further, when an EMF is applied across i, the magnetic elements M are accelerated in a direction depending upon the direction of the current. 
         [0081]    As stated, the air passes from the first volute V 1  and into the first compressor stage C 2  and S 1 . C 2 -C 7  are axial-compressor rotor vanes and each has a root  23  that sits in and is anchored by, in a preferred embodiment, layers of fiber-reinforced plastic or carbon-fiber-epoxy sheets that have been spun around the rotor wall  25 , with the roots temporarily attached, and cured, permanently and durably fastening the compressor vanes C 2 -C 7  to the rotor wall. The strength of this bond is important as the system will rotate at extremely high velocities. The stator vanes S 1 -S 5  are traditional stator vanes and are interspersed with the compressor vanes C 2 -C 7 . Each compressor vane C 2 -C 7  is embedded with a magnetic element M which interacts with conductive coils i in the same way as described in the preceding paragraph. The magnetic elements M, the fiber/resin layers  24 , and the bodies of the compressor vanes C 2 -C 7  make up the greater part of the mass of the rotor of the second compressor group, and thus form a flywheel as do corresponding elements of the first compressor group  2 , and by much of those items being magnetic, also form a generator. It is here noted that  30  indicates an annular disk with solid, structural elements  26  and  29 , and passageways S 6 , C 8 , C 9 , and T 3 . The gases exiting the last turbine stage pass through stator S 6  and then to a passage, also vaned, to turn and pass through a stator C 8 , which is here labeled as a compressor stage C 8  because the air, being entrained within the body of rotor  28 ,  25 ,  42 ,  45  etc. at this point, will see the stator C 8  as a compressive stage C 8 , and will be further compressed such that when it passes to rotating passage  45 , it seems stationary in the relative frame of the rotor as if it had just passed through a single compressor stage. Now arrived at passage  45 , said air passes leftward, as seen in  FIGS. 2 , and  45  becomes a manifold whereby an annular passageway  45  is divided into dozens of sector-shaped passages  47  interspersed with sector-shaped passages  48  which carry exhaust that is downstream of the combustor. This is the recuperator R, whereby the thin walls separating  47  and  48  (the dotted lines for  48  indicate that the cross-section used for  FIG. 2  is in the plane of the compressor side sectors  47 , which are shown with solid lines) pass heat from the combustor-downstream sectors  48  to the air in the air currently under discussion, raising its temperature and thus, performing work on it and taking work from the turbine side. 
         [0082]    The air enters another manifold where it merges back into an annular passageway and enters another stator C 9 , which for the same reasons given for C 8  is treated as a compressor stage. The edges of the entry and exit vanes of  45  and  53  should be bent to an angle to complement such a relationship with the stator vanes C 8  and C 9 , as should the edges of passageways  40 ,  41 , and  44 . The air now enters a passageway  40  where it is again flung outwardly (this could be seen as a compressive stage but the air therein is only regaining the energy it lost by being pushed toward the axis  50  in  27  and R to begin with, so this will not be discussed). The air enters a stator S 7  where it is deflected to a proper exit angle to act on C 10 , which with C 11  make up the final two compressor stages  39 , separated by another stator S 8 . By the time the air enters the combustor C through passage  33 , it will have been acted upon by approximately 11 compressor stages, one of which is a large centrifugal compressor, such that with the recuperator R the enthalpic rise should be the equivalent of at least a 14-stage axial compressor. It is mentioned in passing that the recuperator and change-of-direction passageways can be done without and the air could simply pass from S 6  to  33 . The more complicated embodiment has been included for patent purposes for it inherently comprises all the elements of the simpler ones.  31  depicts the outer edge of rotor segment  42 . The rotor has been divided up into segments  2 ,  48 ,  47 , and  46  to show that during manufacture it can be stacked and that it would not be required to perform the impossible, which would be to have the rotor formed whole. In the event that  30 , the turning passages, and the recuperator R were removed from the concept, these considerations would be less profound. It is also envisioned that annular segment  30  could extend all the way to axis  50  and  42  would be a third compressor/turbine/generator/flywheel rotating independently of  2 / 5 / 6  and  3 / 4 / 7 , but in this case it is uncertain at this time what turbine would drive compressor stages C 2 -C 7 . 
         [0083]    Continuing with the discussion of the rotor depicted by reference numerals  42 ,  28 , and  31 , more magnetic elements are spaced around the periphery near  31  and interact with conductive coils i, as previously described.  28  and  42  are not actually solid, but insofar as the air is concerned, they are. The air enters the combustor at  33  where it passes into the combustion chamber through nozzles  34  and it is ignited by a fuel mix coming from fuel burner nozzle  32 .  35  are flame propagation nozzles that contribute to forming the flame and preventing the flame from passing upstream. This is well known in the art. The exhaust of the combustor passes through  36  to impinge on first turbine stage T 1  which in this embodiment is of a piece with C 11 , as is S 9  with S 8 , T 2  with C 10 , and S 10  with S 7 . This arrangement is hoped to save space and allow the radial compressor stages and turbine stages to coexist and be advantageously located radially inwardly of the combustor and at the end of the machine. Wall  37 , with  21 , completes the outer casing of the device. 
         [0084]    The stators  38  of the first two turbine stages could easily be made to swivel via a simple ring gear to be variable stator vanes, allowing it to change the flow characteristics through the first turbine group  4  to adjust for different altitudes and rates of combustion. The air passes from first turbine group  4  to another passageway  41  which delivers it to another stator T 3  which for the same reasons as C 8  and C 9 , is being treated as a turbine stage. Although counterintuitive and hard to understand, the laws of gas turbine engine theory can be used to prove that energy is recovered from the exhaust stream here (as it is provided by C 8  and C 9 ), and although it is not the intention of the present application to define this, the inventor sees this as far simpler than describing how it is actually  27 ,  45 ,  40 ,  41 , etc. that are absorbing and performing the work. The virtual enthalpic ratio across T 3  can be seen as approximately 1.4:1, and the same goes for C 8  and C 9 . From T 3  the exhaust enters another manifold  44  which splices with manifold  43  to create the sectored recuperator R described above. Element  49  exists in the compression side  58  of sectors  47  and is used to guide the flow from  45  to  43 , bringing it out in an opposite axial direction from how it entered. However, no such element is used in the turbine side sectors  47  because the air from T 3  moves more or less axially to arrive at another manifold, also indicated as  44 , to be fed into the second volute, V 2 . It is noted at this time that V 1  and V 2 , as well as any space or substance between them, are part of an annular body  57  that is fixed to the casing  21  and extends radially inwardly therefrom. Like V 1 , volute V 2  can also have a diffuser D 2  or some type of swirling or anti-swirling vanes, and is integrally vaned to evince some type of indescribable, despite conceived efforts, stator vane which serves as a volute for the fourth and final turbine stage, T 4 , which is the sole representative, in the preferred embodiment, of the second turbine group  5 . T 4  and C 1  are locked for rotation with each other and sit on a spindle  52 , which nests around shaft  53  which is integral with the rotor  42 ,  46 , etc. at  51 . Spindle is separated from the main rotor  42 ,  53 , etc. by bearings B to define a space  45 . It is unknown at this time what type of bearings would be most cost-effective, but of course the idyllic embodiment would be levitational-bearings (alternating magnetic fields facing each other creating constant repulsion).  54  defines the output shaft and is integral, in the preferred embodiment, with  42 ,  53 , etc. The overall machine is quite small, so it is not unforeseen that  54  could be cast or forged with  42 . The air exiting T 4  passes to outlet. 
         [0085]    In operation,  5  drives  2  and  6 , and  4  drives  7  and  3 . Any force on  5  will be communicated to  2  and  6 , any force on  2  will be communicated to  5  and  6 , etc. Any force on  4  will be communicated to  7  and  3 , etc. This is why  5 ,  2 , and  6  are shown in  FIG. 1  to be on a virtual shaft, although there is no shaft, they are integral. The same goes for  4 ,  7 , and  3 . This is why the device is called an integral gas turbine, flywheel, and generator. 
         [0086]    It is noted that to ease understanding of the invention, one would be well advised to skip the discussions of  FIGS. 3-5  and return to them only when a fuller understanding of the overarching concepts has been established. They are not directly claimed in the present application. However, for disclosure and best-mode purposes, as well as to provide basis for being claimed in later applications, it is necessary to describe them now. 
         [0087]      FIG. 3  shows pump/motor PM 1  and motor/generator MG 1 . Air enters this system from PA 1  via  76  and immediately encounters a three-way, three-position valve that serves to close PM 1 , send gases to a turbine  82  via path  79 , or bypass the turbine and, along path  78 , send gases directly to the piston cylinders  70 - 72  that make up the vital portion  73  of PM 1 . The air entering the turbine enters through a standard volute V 3  and exits at  81 . After  81  the air enters a distributor  75  that is actually represented by  FIG. 4  and is not simply an entrance manifold.  70 - 72  become progressively larger and the air is successively expanded, after (or not) being expanded in the turbine, through these three stages, and harnessed for work thereby. The piston rods  74  turn a crankshaft  83  at  80 , on which is also disposed the turbine  82  and the mechanism by which the turbine powers the crankshaft. Extending from turbine  82  is a stub which is notched all the way around to make a sun gear  84 . Around the sun gear are orbital or planetary gears  89  that engage the teeth of the sun gear and rotate on planet carrier  85  which can be braked by  87 . The output of the planetary gears is passed along to the ring gear  86  which is fixed to the crankshaft  83 . This type of gear reduction is well known in the art and needs not be defined here, save to state that braking and de-braking the carrier  85  leads to two different step-down ratios, such that the turbine should be able to drive the shaft over two distinct or overlapping ranges of pressurization upstream of the turbine. At these (relatively higher) PA 1  pressures, the exhaust from turbine  82  passes to  75 . At lower PA 1  pressures the turbine becomes useless and  77  is switched to path  78 . Regardless of whether the turbine has bee cut in or out at  77 , the exhaust now expands in  70 ,  71 , and  71 . At relatively higher pressures it may be advantageous to expand the exhaust through  70 - 72  in succession, and that is why  72  is shown as larger than  71 ,  71  is shown larger than  70 , etc. However, after drawing  FIGS. 3 and 4  the inventor, upon weighing both alternatives, believes that the best embodiment for PM 1  would be to pass the exhaust through all of the piston-cylinders in parallel and forego the turbine during hybrid operation (described later). Exhaust would simply be valved in on the pressure side of the cylinder at a pressure slightly above the ambient pressure (the outlets of the piston-cylinder arrangement communicate with ambient air). The control of this valving will be of vital importance, for if done properly the pressure drop across the cylinder can be kept as low as possible, and the movement of the piston rods as slow as possible, maximizing the energy rendered. 
         [0088]    The driven parts  74  and  86  drive the crankshaft which, on the left end, is surrounded by a sleeve  93  which is further surrounded, at two points, by outer sleeves  94  and  104 . Outer sleeve  104  can be clutched to crankshaft  83  by clutch  103 , locking the rotor  105  of the motor/generator MG 1  for rotation with the crankshaft. Clutch  102  locks  105  for rotation with sleeve  93 , which is clutched, via a direction-reversing arrangement, to an output pulley  96 , which with belt  107  and axle pulley  108 , comprise a continuously variable transmission (CVT) of known type. The outer periphery of sleeve  94  is splined and carries, on each side of output pulley  96 , sun gears that cooperate with planetary systems  92  and  97 , one of which has a single ring of planet gears and the other has a double ring of planet gears, such that the ring gears  99  and  91  will be driven in opposite directions from each other, inverting the drive relationship between  107  and  83  depending on whether clutch  91  locks  100  for rotation to sleeve  93  or clutch  101  locks  100  for rotation with sleeve  93 . Clutch  90  locks the sleeve  93  for rotation with crankshaft  83 . It will be apparent to one skilled in the art that the piston rods  74  can drive MG 1  without connecting to the CVT, the CVT can drive MG 1  (or vice versa) without connecting to the piston rods or the turbine  82 , and the piston rods and/or turbine can drive the CVT (or vice versa) without connecting to MG 1 .  109  is a service brake and will be used when loading the axle  88  via PM 1  and MG 1  is insufficient for achieving the desired braking force.  106  is the stator coil of the motor/generator MG 1  and its polarity will be oscillated and inverted to energize or be energized by the rotor  104 . 
         [0089]      FIGS. 4 and 5  describe how the air from PA 1  can be sent to the expansion modules  70 ,  71 ,  72 , and  82  in different modes of operation. Theory will be foregone at this point and the parts described. The device works as shown in  FIG. 5  and only a description of the parts will be made here.  77  is the same three-way valve from  FIG. 3 , cutting in or out the turbine  82 . A check valve  120  is provided in outlet  81  of turbine  82  to prevent backflow. Before valve  124 , line  78  splits off on line  121  to enter the inlet  125  of piston cylinder  70 . Switch  122  inverts the relationship between inlet  125  and outlet  126 , such that first one side (top) of  70  is the pressure side, and then when the piston has traversed the cylinder, that side (top) becomes the relief side. The return line  123  enters valve  124  in parallel with line  78 . Valve  124  switches the feed from lines  78  and  123  to lines  127  and  131  as shown by the arrows associated with a and b.  128 ,  129 , and  130  are exactly the same as  121 ,  123 , and  122 , respectively. Valve  132  can only be described by directing a reader to the arrows of a, b, and c and allowing them to be imagined in each of their three settings as relates to lines  133  and  134 . These types of valves are known in the art and would unduly encumber the disclosure if an attempt were to be made to describe them. In short, the air arriving from  137  can arrive there after being passed through the cylinders and turbine according to the modes  140 - 145  in  FIG. 5 , each being a combination of valve settings which cause series or parallel or hybrid series-parallel flow through the piston-cylinders, depending on the pressure within PA 1  and the power output requirements of PM 1 , as well as external concerns. 
         [0090]      FIGS. 6-8  correspond to  FIG. 9 , which shows a vehicle according to the first embodiment of the invention as if the top were removed revealing the internals. TF is the turbine/flywheel of  FIG. 2 , and MG 1  and PM 1  are the same as those from  FIGS. 1 and 3 . Turning first to  FIG. 9 , the body of the vehicle is shown as  238 . Seats  227  are provided for passengers in the event that this is a passenger vehicle. An electric motor  251  is provided, now taking the place of the load L, for each of the rear wheels and communicates with the electrical bus of  FIG. 1 . A cowl  212  encases a fan or propeller  210 . Wheels  234  are steering wheels and are connected to the drive axle  88  and, thereby, to PM 1  and MG 1 . Pitch/roll/yaw stabilization nozzle housings  239  are on the front corners of the vehicle, and vertically sweeping radar modules  241  are provided to sense the orientation of obstacles and terrain relative to both front corners of the vehicle.  232  is a camera to provide a dash display of the field of view that the driver cannot see, more or less that below and before the vehicle.  201  is an intake manifold for the turbine/flywheel TF, and  206  is a plate heat exchanger for the TF&#39;s exhaust to thermally communicate with its intake.  209  is the drive shaft for the fan and it can directly couple to the output shaft  54  of the TF. Lines  6 - 6 ,  7 - 7 , and  8 - 8  relate to the cross-sectional cutaway  FIGS. 6-8 , respectively, and show approximately where  FIGS. 6-8  pertain across the lateral extent of the vehicle. 
         [0091]    Turning to  FIG. 6 , the dotted line  229  surrounding the vehicle is included to show that the major expanse of the vehicle&#39;s body  230  conforms to the shape, as nearly as possible, of an ideal airfoil. The flap  225  folds up, to spoil this shape and cancel lift, and down; ro complete this shape such that, given sufficient thrust and pitch/yaw/roll stabilization, the vehicle will automatically become airborne. PA 1  commandeers every cubic inch of the vehicle not needed for personal use. The larger it is, the more gas it can store, the more efficient the system becomes.  224  is the back wall of the vehicle and holds  226 , which is the hinge upon which flap  225  pivots.  231  is a fuel tank.  233  is the dash and control module of the vehicle, and  228  is hoped to show the creation of leg-room for occupants of the vehicle. All ergonomic considerations cannot be dealt with in this application, and therefore have been mostly omitted. 
         [0092]      FIG. 8  shows what the vehicle of the first embodiment might look like from the side. It does not look like an airfoil because of panel  237 , and it is assumed that this will be pleasing to a customer, that his/her car not look outlandish.  225  is shown in its upright configuration, and a spoiler fin  235  shows other aspects that might be added for aesthetic purposes, as well as to offer a moment to expound on other features that might be desirable. Such as, although no one wants wings on their car, it might prove optimal to locate other airfoil-shaped objects around the vehicle to supplement lift and stability. Also, from the spoiler shown a tail-fin might be made to pop up, providing a good location to implement a rudder. It is doubtful the vehicle would be stable without a rudder. Dashed line  236  indicates the location of back wall  224  on the other side of panel  237 .  238  is meant to be the main body of the cabin, comprising doors, roof, etc. Pitch/yaw/roll stabilization nozzle housings each have three nozzles  140 , selectively actuated, allowing bursts of gas to escape PA 1  upwardly, downwardly, and laterally outwardly, from each corner of the vehicle. It is believed that with no great amount of computing power, a 6 D.O.F. accelerometer/gyrometer and the proper algorithm, unwarranted pitching, yawing, and rolling can be offset and smooth air travel experienced. In all of  FIGS. 6-8 ,  221  represents the inhabitable space of the interior of the vehicle. 
         [0093]      FIG. 7  shows the preferred embodiment for implementing the system of  FIG. 1 . Air is taken in at the inlet  201  and passes through plate heat exchanger  206  where it experiences thermal exchange with the exhaust from the TF, which is forced down into PA 1  by  202  and is shown as arrow  203  coming out of the heat exchanger into the pressure accumulator. From  206  the air enters the TF via a manifold  219 , which takes the concentrically arranged inlet and outlet streams from the TF and places them in alternating passages, making heat exchange more efficient and simplifying the device  20 , which is a seal, having two positions, and by sliding it up and down the controller can close simultaneously the inlet and outlet of the TF, or simultaneously open them.  70  and  71  are shown to represent the piston-cylinder array  73  of PM 1  and  108  is the drive pulley on the drive axle,  107  being the belt of the CVT.  204  is a thrust reverser for the intake air, and can be opened while  201  is closed to take in air vertically instead of horizontally. 
         [0094]    A vertical take-of valve VTOV is provided to send air, through bore  205 , through outlets A, B, and C. By controlling it, gases from PA 1  escape therefrom at high velocities, modifying the thrust vector of the vehicle overall. Passage A sends the gases rearwardly where they escape at  216  and supplement thrust of the fan.  217  is a panel with outlets which can be opened such that air  218  is directed downward, in the event this device is to be used as a hovercraft or hydrofoil. Although this is foreseen, it is not a subject of the present application. Position B directs gases directly downwardly. Position C directs gases downwardly and forwardly, also acting as a thrust reverser to be used with  204  in certain applications. 
         [0095]    The right-hand side of  FIG. 7  depicts a vertical take-off module comprising manipulable flaps  213 , flap panel  215  having tracks for the flaps  213 , and the fan casing  212  and hub  211 . Airstreams are shown to portray how each of the panels in its different position affects the air through and out of the turbine. Vertical panels  214  pop up from the flap panel  215  when it is fully extended and before the flaps  213  are moved up. These panels  214  serve as outlet guide vanes for the turbine and disallow stream migration and surge when the flaps are in different positions from each other. A rotational shaft-to-shaft coupling  208  allows connection of the TF to the drive shaft  209  to drive the fan. The output shaft  54  of the TF is as short as possible. It possesses trunnions or splines that mate with corresponding female members on the inside of a sleeve or collar that can be slid, in the direction of the arrow shown by  208 , over the output shaft, such that the trunnions or splines drive the collar or sleeve, which in turn drives, through reduction gearing similar to that shown in  FIG. 3 , the drive shaft and thence the fan. 
         [0096]      FIG. 10  shows a rear view of the components of  FIGS. 6-9  and will not be explained again except in those reference numerals that were not explained above. Namely, that the flaps  213  can assume any imaginable combination of angles, such as a controller might deem appropriate for vector nozzling the fan thrust. Also, that  223  dips down farther than  224  by the inlet of the fan, but no more than necessary. Also, that ailerons  242  have been considered but it is unknown at this time whether they will be necessary, due to item  239 . However, in the event that they were desirable, they would pivot as shown by arrow  243 .  FIG. 10  has been included to exhibit the extent to which the airfoil shape can be effected while preserving an unobjectionable shape for the overall vehicle. 
         [0097]      FIG. 11  is exactly what its title says. This is how the system will operate from origin to destination, in normal day-to-day ground travel. The steps have been listed here for disclosure purposes. It is noted with emphasis that the last step of the method charges the PA 1  and seals it off, such that when an operator starts the vehicle again, the first can be performed. 
         [0098]    1.) Start-Up: 
         [0000]    Depressurize pressure-accumulator PA 1  through reversible pump-motor PM 1 .
 
Route generated electricity from PM 1  to conductive coils (i), accelerating TF.
 
Open inlet and outlet of TF.
 
Commence combustion in combustor C.
 
         [0099]    2.) Run-Up and Hybrid Operation with P&gt;Pmin: 
         [0000]    Combust until ω 1  (TF rotational velocity  1 ) and P 1  are reached (load can be energized at this time)
 
When P=P 1 , close inlet and outlet of TF.
 
Compressors and turbines self-evacuate with assistance from pump and relieved (open) bias-seals.
 
Slowly expand gases in PA 1  through PM 1  (currently a motor-generator), electrically accelerating TF.
 
Deceleration of TF via energization of Load L.
 
Acceleration of TF via braking of Load L.
 
Successive reiteration of steps 2-5 and 2-6 until P=Pmin (or insufficient upcoming brakings foreseen).
 
Meanwhile, during quick-stops (brake-force required larger than reverse load capacity of load L):
 
Reverse PM 1  (now a pump), utilizing supplemental brake-force to draw ambient air into PA (Supplemental braking requirements excessive) Activate service brake.
 
When P=Pmin OR oil=ω 1  min (or insufficient upcoming brakings foreseen)—go to step 1-3.
 
         [0100]    3.) Shutdown/Parking: 
         [0000]    Close (if open) inlet and outlet of TF.
 
Route electrical energy from TF to PM 1 .
 
Reverse PM 1  to pump ambient air into PA.
 
When ω 1 =0, close PM 1 —resulting in hermetically sealed PA with sufficient charge to begin step 1.
 
         [0101]      FIGS. 12 and 13  get a little more involved, but again there is no need to explain an explanation. The best way to understand the first embodiment is to mentally trace these steps (above and below) and although these are special cases of usage, they fulfill the inventor&#39;s obligations of best mode, enablement, and industrial applicability. Each routine, as in scenarios 1-3 above, is best described by its heading. 
         [0102]    4.) Starting from Road Travel with Moderate ω at Decision Moment (i.e. Typical Highway Lift-Off): 
         [0000]    Close (if open) PM 1 , sealing PA 1  (vertical take-off valve VTOV already closed).
 
Open (if not already open) inlet and outlet of TF and commence combustion (if not already combusting).
 
While P increases to Pmax, direct all electrical energy from TF to load L, accelerating vehicle.
 
When P=Pmax, cease combustion, close inlet and outlet of TF, open fan F inlet and flap panel to idle fan.
 
Electrically transfer all kinetic (rotational) energy from TF module  1  (TFM 1 ) to TF module  2  (TFM 2 ) and L.
 
When TFM 1  and F are rotationally matched (via reduction gearing ratio), slide collar over trunnion.
 
Open PM 1  to maximum throughput, transfer all energy from PM 1  and TFM 2  to TFM 1  and L (until/unless vehicle velocity is near lift-off velocity, then deactivate L for duration of flight)
 
Open inlet and outlet to TF, commence combustion, positively drive F at lift-off thrust Although PM 1  is still at max throughput, P will quickly reach Pmax).
 
Selectively open vertical take-off valve VTOV to position A to complement fan thrust and to waste-gate PM 1 .
 
If advantageous, momentarily (or for duration of lift-off) rotate VTOV partially/fully to position B and vertical take-off flap VTOF partially/fully upright to achieve “pop up” effect.
 
         [0103]    5.) Starting from Road Travel with Excessive ω at Decision Moment (i.e. Atypical Highway Lift-Off): 
         [0000]    Reverse PM 1  (now a pump) and slow TF electrically via PM 1  and L, charging PA 1  and accelerating vehicle.
 
When possible, open inlet and outlet of TF without combustion, further charging PA 1  and slowing TF.
 
When ω falls to predetermined rate, commence combustion;
 
Go to step 4-3.
 
         [0104]    6.) VTO with Moderate ω (i.e. Heliopad/Driveway Lift-Off): 
         [0000]    Down flap panel, open fan inlet, open inlet and outlet of TF, commence combustion, charging PA 1 .
 
Direct some electrical energy from TF to reversed PM 1  (now a pump), further charging PA 1 .
 
When P=Pmax, cease combustion, close inlet and outlet of TF, close PM 1 .
 
Electrically transfer all kinetic (rotational) energy from TF module  1  (TFM 1 ) to TF module  2  (TFM 2 ) and L.
 
Service brake applied (connect to front axle, PM 1  pistons connect to generator) anytime prior to step 6-7.
 
When TFM 1  is completely stopped, slide collar over trunnion, raise VTOFs to near-upright (fan nozzled down).
 
Open inlet and outlet to TF, commence combustion, continue to reverse PM 1  via electricity from TF.
 
When P=Pvto, quickly cycle VTOV to position C and switch to thrust reverser on front inlet.
 
One VTOF has been left horizontal to keep down-thrust just shy of lift-off. It is now raised parallel to the others.
 
         [0105]    7.) VTO with High ω (i.e. Traffic Lift-Off): 
         [0000]    Reverse PM 1  (now a pump) and slow TF electrically via PM 1 , charging PA 1 .
 
When ω falls to predetermined rate, go to step 6-1.
 
         [0106]    8.) Pre-Planned or Taxi-to-Runway Flight (Since Significant Fuel is Consumed by VTO, this May be Common): 
         [0000]    Perform steps 1-1 through 2-7 until on straightaway/runway, then perform steps 4-1 through 4-11.
 
With (GPS) knowledge of route (user&#39;s home and favorite lift-off), the computer can optimize fuel usage.
 
         [0107]    9.) Road Landing: 
         [0000]    Obtain altitude and alignment just above roadway, level out and run TF and F at cruise.
 
Raise the central VTOF, or two outermost VTOFs, partway, to partially vector the thrust down Simultaneously with 9-2, cycle VTOV to position B.
 
Loss of thrust in 9-2 and 9-3 reduces lift. Vehicle descends onto air cushion created by downward thrust.
 
Several inches above roadway, level VTOFs and retract (toward fan) flap panel. Rear wheels touch down.
 
A moment behind step 9-5, cycle VTOV closed and cease combustion. Front wheels touch down. Slide collar off trunnion, close fan inlet.
 
Braking load drives TF to high ω, go to step 2-5.
 
(it is uncertain at this time when, whether, and how PM 1  should be utilized during this procedure)
 
         [0108]    10.) Vertical Landing: 
         [0000]    Obtain approach position, attitude, and altitude.
 
Cycle VTOV to position B and all VTOF&#39;s to max upright position, vectoring all thrust and exhaust downward.
 
Pitch/roll/yaw nozzles PRYNs and TF driven selectively to stabilize speed, lift, pitch, roll, and yaw
 
Vehicle coasts through a deceleration and descent curve to arrive mostly slowed, above and just shy of LZ.
 
Cycle VTOV to position C and switch to thrust reverser on front inlet, bring horizontal velocity to zero above LZ.
 
Attenuate fuel-in until touchdown.
 
Slide collar off trunnion, close VTOV, retract (toward fan) flap panel, close fan inlet.
 
Go to either step 2-1 (to taxi or drive) or step 3-1 (to park).
 
         [0109]    11.) Other Features: 
         [0000]    With GPS device, system can begin shedding energy a certain distance from one&#39;s destination. Docking station plug-ins allow vehicle to depart with maximum ω and P, such that lift-off happens fully fueled. 
         [0110]    Although the method is extremely complicated, it is believed by the inventor that with the capabilities of modern computers, a simple device with very few moving parts and a complicated control method is preferable to an inordinately complicated device (think vertically thrusting fan geared to main drive shaft) with a simple control method. Some compromise must be made in pursuing vertical take-off and landing, and the inventor believes he has not put forth more requirements on the controller than a modern lap-top computer could handle. 
         [0111]    Continuing now to some essential attributes of the TF that were not mentioned earlier.  FIG. 14  shows a typical axial-flow compressor vane. It is believed that no special shape will be needed for implementing the TF, however, as shown in  FIG. 15 , the inventor believes the preferred embodiment and best mode at this time are represented by a magnetic core  62  encased in the vane  63 . U.S. Pat. No. 5,179,872 to Pernice provides for a magneto rotor having magnetic elements in pockets and the method of Pernice seems to be the best mode for achieving a workable model of  FIG. 15. 62  would be an alloy of 33%-64% Nd/Fe (neodymium/iron) encased in, sintered in, or otherwise retained in aluminum vane  63 . It is likely that the vast majority of TF will be of aluminum. As for the conductive coils in the casing of the TF, there are many ways to do this, and such is not the subject of the invention. What is important is that it be modified from encompassing the magneto or dynamo, as is usual in the art, and the loops tightened and multiplied to account for so many magnets. It goes without saying that in every aspect of this embodiment, the lightest materials are preferable. 
         [0112]      FIG. 16  shows a feature necessary for sealing air passages from nearby air passages within the TF. When combustion is stopped, typical seals would create friction, slowing the rotors and being a detriment to the flywheeling thereof. Therefore seals  60  (they are all over  FIG. 2  but not shown, as they are small) are strategically place such that when combustion ceases and the pressures inside the system diminish, the seals disengage from their land. They would be biased away from the land like a Belleville washer spring and the high pressures during combustion would close them. This requires that an analysis be made of the pressures throughout the system, such that the seal always face the right direction. Once properly placed, it is inherent that once combustion ceases, the seals would open and, all gases would migrate from areas of high pressure to areas of low pressure, and almost all flow in radial passages should be outward. That way, the entire system can be evacuated by draining the combustor with evacuation pump  8 . 
         [0113]      FIG. 17  shows the environment within which could be implemented through a second embodiment of the invention. The method is different and there are no magnets, but much of the rest of the system is the same. The concepts of the first invention have been extrapolated and modified to create an airplane capable of vertical take-off and landing. Aircraft  300  has within its wings  301  compartments  302   a - c  (and  302   d - f  in the other wing, not labeled). The compartments or chambers are separated by walls  303 ,  304  which might or might not have an opening for unobstructed migration of air between compartments. Gas turbine engine  305  is no longer called a TF and will be treated like any other gas turbine engine. Again,  70 - 72  are piston-cylinders that drive, like in PM 1 , a drive arrangement  306 . Flaps and ailerons and panels  213 - 215  correspond to those in the first embodiment. 
         [0114]      FIG. 18  is a cross-section taken along the wing  301  of the aircraft  300 . Intake  301  passes air to the gas turbine engine  305 . For simplicity, the gas turbine engine of  FIG. 2  will be assumed to be within the housing of  305 , except now it sits upright on a vertical shaft  331  (this was the embodiment originally designed for embodiment  1 , as evinced by the provisional application, but the bevel-gears and entailing mass were thought to be of diminishing returns, however it would spin like a top). An outlet  303  leads either to a simple outlet diffuser  302  which results in the exhaust pressurizing the wing, like the pressure accumulator of the first embodiment. At  308  air enters a series of piston-cylinders  325  either in series or parallel, as explained before, and with an outlet at  324 . The piston rods  326  turn a crank within  327  which turns bevel gear which drives bevel gear  305  which is fixed for rotation on the main shaft  307 . Main shaft  307  is also driven by a bevel gear  304  which is driven by a toothed annular strip  329  on top of the first compressor stage. The vertical take-off nozzle  339  passes air selectively from inside the wing, through bore  340  to outlets  336 ,  337 , and  338 . These correspond to positions A-C of the first embodiment. A hydraulic pump  334  drives through a reversing valve  335 , a hydraulic system that drives inner shaft  311  telescopically inside outer shaft  307 . The inner shaft  311  has seals  310  which allow it to act like a piston inside the outer shaft  307 . The inner shaft is threaded and knobbed at the end, the threads being shown at  312 . The fan cowl  315  has an implement  314  atop it for cooperating with the inner shaft  311  to open and close the fan. Dashed line  322  shows the fan cowling in its dropped position. This is a non-use position for the fan. VTO flaps  316  and flap panel  317 , as well as ailerons  318 , perform as described in the prior embodiment.  319  is the exhaust from the piston-cylinders.  320  is the hinge for the ailerons and  321  is the hinge for the flap panel. 
         [0115]      FIG. 18  begins to make sense when viewed in conjunction with  FIG. 19 .  FIG. 19  shows the top of the wing, the niche  355  for accepting the cowling in the non-use position, the hinge  354  for the cowling, the fan  349 , and flaps  353  in their non-VTO orientations.  346  shows that the cowling is not just a box but really, all the way around, hollow with strut-vanes that direct air and support the fan.  347  and  348  are directed to the aforementioned scheme of using the telescoping shaft to hide or expose the fan.  347  is a slot through which the tip of  311  is passed during manufacture. It tapers to a neck at the end of the threaded portion and a knob is supplied such that the neck slides within the knob, but the knob and threaded portion limit the movement of the slot on the shaft. As the shaft  311  extends, the ramp of  314 , now seated in slot  357  with its tip wrapping around the neck of the shaft, will cause the cowling to raise and pivot up. When the cowling becomes upright and the shaft is now completely extended (reference numeral  356 ), the shaft begins to turn and screws the threaded portion into the hub of the fan. After operation, the pump-motor  327  can be reversed to unscrew it. Then, upon retraction, the knob will pull the slot with it, collapsing the fan into the wing.  345  shows the ailerons in their relation to the flaps  353 .  358  and  359  are mounting arrangements for the shaft. 
         [0116]    Inside the wing, the gas turbine engine reposes as shown in  FIG. 20 .  FIGS. 20-22  serve to also show the different views of the combustor and will be nearly identical to how it will appear on the TF of  FIG. 2 . It is again here called TF because it is universal to the present application in all embodiments. TF has a top  363  of its housing which encases the centrifugal compressor and turbine, whose inlet and outlet are, respectively,  364  and  365 .  361  corresponds to  33  in  FIG. 2  and is the passage from the last compressor stage output into the combustor C or  362 .  360  is the guide structure for leading air from the combustion chamber C to strike the vanes of T 1 . This is shown in  FIG. 21  and includes vanes  372  and  373 .  371  is the space between the outer wall of  362  and the combustion chamber geometry  370 , and assists in surrounding the chamber with air to be led into it.  FIG. 22  shows four guide structures  375  leading to four combustion areas  374 . It is noted that the combustor inlet  361  would appear like a mirror image of  FIG. 21  if portrayed. 
         [0117]    At the top of  FIG. 20  is an arrangement for placing all of the units within the wing in communication with each other. The inlet to the combustor communicates with this rail via path  369 , as the turbine outlet does via  368 . The combustor inlet  361  and outlet  360  communicate with the rail along path  366  and  367  and  366   a  and  367   a , respectively. All four of these paths connect to the rail, which has a tube for each of the four airflows.  379  is a turreted, cylindrical valve with openings designed to transfer, at different degrees of rotation, the flow between any one passage and any other, and between any of them and, through the openings shown in the exposed portion of the rail, with the pressure accumulator. Each longitudinal zone of this valve will have a different set of borings, such that when the valve is turned a certain amount in one direction, the airflow seen in  FIG. 23  becomes realized. Turning a little more would yield  FIG. 24 , and a little more would yield  FIG. 25 , and so on for further utilizations. The different schemes shown for driving different compressors with different turbines and different turbines or compressors with different pump-motors are by no means to be considered exhaustive. There are likely dozens of scenarios whereby the various compressors and turbines and pump-motors of the several units could be valved to enhance the efficiency. But to begin with, the maximum power output would be all units running full, with cowlings up and flaps down, for vertical take-off. The extra scenarios are envisioned for achieving different cruising speeds while minimizing fuel burn. 
         [0118]    Claims  26  show a third embodiment of the invention.  402  is again the TF from the first embodiment. The inlet  401  has no special features and the turbine outlet could go anywhere into the body  400  which is a pressure accumulator except where the cabin resides.  403  is a drive arrangement and transmission for coupling the output shaft of the TF directly to the drive wheels of the vehicle, which is a little tow truck. It can hardly be considered a truck going by the dimensions shown in  FIG. 27. 409  indicates the cabin and  405  indicates the airflow from the pressure accumulator to a bank of pump motors  407  stored in the tongue of the truck. The driven wheels are oversized relative to the truck because they must support the weight of a towed object, as described later.  410  is the bulk of the pressure accumulator. This is a collapsible chamber that when extended takes the form shown in  FIG. 26  and when collapsed takes the shape shown in  FIG. 27 . The tongue  413 ,  406  is adapted to have its wheels  411  attached  412  and removed via a slide-up arrangement  414  which lets the axles slip up and out when a pin is pulled out. 
         [0119]    In operation the truck drives around in hybrid mode, answering to a dispatch service. It should get the gas mileage of a very small car operating with the pressure accumulator  410  very large such that the TF pumps it full and it can drive around for a substantial time before requiring recharge. However, when the truck arrives at the scene of a vehicle  418  to be towed, the chamber collapses to the configuration shown in  FIG. 27 , and the tow truck assumes a position directly in front of the vehicle  418 . The operator removes the wheels and the tongue sinks (any number of mechanisms can be used to soften this and/or protect the tongue) to the road and the tow truck backs up, resulting in the tongue extending partway under the vehicle  418  and between its front wheels. The operator throws a strap  416  over the hood of the vehicle  418  and ratchets it down as per the arrow  417 . The TF then commences combustion and charges the pressure accumulator  410  against the undercarriage of the vehicle  418 . Once a pressure of 3 or 5 atmospheres has been reached (3 atmospheres is 2 atm over barometric, which will yield 28 psi in force, easily jacking even the largest vehicle and if not the pressure will reach many more atmospheres before the pump/motor is activated), the expanding chamber  410  causes a torque  415  about the back rim of the tongue and the configuration shown in  FIG. 28  will be soon reached. The tow truck now operates as does the first embodiment during flight, with adjustments for the transmission and other requisite accoutrement. The TF will be very powerful compared to the tow truck&#39;s weight itself, but would be set to match the horsepower of a large truck, which is generally less than 500 HP, such that the turbine should not have to be very large. The pump/motors will continue to operate in this condition but slightly differently from the first embodiment. 
       Appendix I 
       [0120]    Of the types of expanders foreseen as the pump/motor (PM 1 ) are: 
         [0000]    a) a single piston-cylinder with one or more control valve(s);
 
b) multiple piston-cylinders with a single, or multiple, control valve(s);
 
c) a single centrifugal turbine of non-variable rotor and/or stator vanes;
 
d) a single centfifugal turbine with variable rotor and/or stator vanes;
 
e) multiple centrifugal turbines of non-variable rotor and/or stator;
 
f) multiple centrifugal turbines of variable rotor and/or stator vanes;
 
g) multiple axial turbines of variable or fixed rotor and/or stator vanes.
 
h) of the foregoing, a+b;
 
i) of the foregoing, a+c;
 
j) of the foregoing, a+d;
 
k) of the foregoing, a+e;
 
l) of the foregoing, a+f;
 
m) of the foregoing, a+g;
 
n) of the foregoing, b+c;
 
o) of the foregoing, b+d;
 
p) of the foregoing, b+e;
 
q) of the foregoing, b+f;
 
r) of the foregoing, b+g;
 
s) of the foregoing, c+d;
 
t) of the foregoing, c+e;
 
u) of the foregoing, c+f;
 
v) of the foregoing, c+g;
 
w) of the foregoing, d+e;
 
x) of the foregoing, d+f;
 
y) of the foregoing, d+g;
 
z) of the foregoing, e+f;
 
aa) of the foregoing, e+g;
 
ab) of the foregoing, a+h;
 
ac) of the foregoing, a+i, a+j, a+k, a+l, a+m, a+n, a+o, a+p, a+q, a+r, a+s, a+t, a+u, a+v, a+w, a+x, a+y, a+z, a+aa, or a+ab;
 
ad) of the foregoing, b+i, b+j, b+k, b+l, b+m, b+n, b+o, b+p, b+q, b+r, b+s, b+t, b+u, b+v, b+w, b+x, b+y, b+z, b+aa, or b+ab;
 
ae) of the foregoing, c+i, c+j, c+k, c+l, c+m, c+n, c+o, c+p, c+q, c+r, c+s, c+t, c+u, c+v, c+w, c+x, c+y, c+z, c+aa, or c+ab;
 
af) of the foregoing, d+i, d+j, d+k, d+l, d+m, d+n, d+o, d+p, d+q, d+r, d+s, d+t, d+u, d+v, d+w, d+x, d+y, d+z, d+aa, or d+ab;
 
ag) of the foregoing, e+i, e+j, e+k, e+l, e+m, e+n, e+o, e+p, e+q, e+r, e+s, e+t, e+u, e+v, e+w, e+x, e+y, e+z, e+aa, or e+ab;
 
ah) of the foregoing, e+i, e+j, e+k, e+l, e+m, e+n, e+o, e+p, e+q, e+r, e+s, e+t, e+u, e+v, e+w, e+x, e+y, e+z, e+aa, or e+ab;
 
ai) of the foregoing, f+i, f+j, f+k, f+l, f+m, f+n, f+o, f+p, f+q, f+r, f+s, f+t, f+u, f+v, f+w, f+x, f+y, f+z, f+aa, or f+ab;
 
aj) of the foregoing, g+i, g+j, g+k, g+l, g+m, g+n, g+o, g+p, g+q, g+r, g+s, g+t, g+u, g+v, g+w, g+x, g+y, g+z, g+aa, or g+ab.