Patent Publication Number: US-2021180474-A1

Title: Turbostirling Engine

Description:
CROSS-REFERENCE TO RELATED APPLICATIONS 
     This application claims the benefit of provisional patent application Ser. No. 62/917,607, filed 2018 Dec. 17 by the present inventor. 
    
    
     BACKGROUND 
     A heat engine is a thermomechanical device that converts part of the heat flow from a high-temperature source to a low-temperature sink into mechanical work. Heat engines currently in common use, such as automobile power plants, are of the internal combustion type. These require a specialized liquid fuel with a narrow range of properties. By contrast, an external-fuel device such as the Stirling engine can use a variety of heat sources, including waste process heat and solar thermal energy. However, being poorly responsive to varying output requirement, the Stirling engine is not suited for directly powering a car. Instead, it is well-adapted for applications where a steadier power delivery is expected, such as for electricity generation from external fuel combustion, for solar thermal power collection, and for waste heat recovery. 
     RELATED ART 
     A conventional Stirling engine includes at least two reciprocating parts, either two pistons, or a piston and a displacer, mechanically connected to a flywheel through a system of crankshaft and pushrods. The piston is exposed on one side to the ambient atmosphere, and the displacer&#39;s pushrod also slides through an opening in the housing. While it is thermodynamically advantageous to use a gaseous working fluid other than air and under high pressure, this arrangement suffers from the difficulty to confine the gas and compensate for the pressure differential. 
     U.S. Pat. No. 4,036,018 to Beale (1977), describes a sealed system that circumvents the problem of working fluid leakage. The reciprocating motions of piston and displacer require special attention to issues of sliding suspension and electronic feedback control of the oscillations. These are addressed in later patents by the same inventor. This design has been adapted for use in space vehicles, and in concentrating thermal solar generators with limited success. 
     Rotary displacers combined with a linear piston are shown in U.S. Pat. No. 8,485,873 B2 to Foster (2013). Different methods have been proposed for using Wankel-type rotary pistons, such as shown in U.S. Pat. No. 3,958,422 to Kelly (1976), U.S. Pat. No. 6,109,040 to Ellison, Jr. et al. (2000), and U.S. Pat. No. 9,086,013 B2 to Franklin (2015). These designs exhibit a substantial degree of complexity, and the eccentric geometry of the rotary elements only offers a partial improvement on the vibration inherent in reciprocating parts and travelling centers of gravity. 
     Advantages 
     The Stirling cycle heat engine of the present invention is of simple construction and can be built requiring only one moving mechanical part. The rotor performs the functions of the piston, displacer, and flywheel individually instantiated in a conventional Stirling engine. There are no articulations or linkages. 
     This motor generates minimal vibration and noise. The only mechanical action involved is the rotation of a symmetrical, fixed-geometry rotor around a fixed axis. There is no reciprocating travel of a physical part, and no significant periodic displacement of the center of gravity. 
     The working fluid in this assembly has no leakage path to the environment through a linear sliding joint since no reciprocating piston is used, eliminating a problem that challenges other Stirling engine designs. 
     This device can be efficiently and compactly implemented in various form factors, from a stackable block externally heated through the combustion of various fuels or concentrated solar irradiation, to a thin plate suitable for operation under solar thermal power, either through direct insolation or as a waste-heat collector underlining a photovoltaic panel, enabling cartop application. 
     This thermomechanical converter can be assembled from as few as three snap-together integral components, suitable for use as an inexpensive scientific toy. 
    
    
     
       DRAWING—FIGURES 
         FIG. 1 —Perspective exploded view of engine 
         FIG. 2 —Detailed perspective view of rotor 
         FIG. 3 —Perspective view of working fluid chamber 
         FIG. 4 —Perspective view of assembled engine 
         FIG. 5 —Perspective exploded view of gasketed engine 
         FIG. 6 —Perspective view of assembled gasketed engine 
         FIG. 7 —Cross-sectional view of engine with rotor in non-stroke position 
         FIG. 8 —Cross-sectional view of engine with rotor entering stroke position 
         FIG. 9 —Cross-sectional view of engine with rotor in stroke position 
         FIG. 10 —Cross-sectional view of engine with rotor leaving stroke position 
         FIG. 11 —Cross-sectional view of engine with offset stroke area 
         FIG. 12 —Cross-sectional view of engine with shaped stroke area and rotor 
         FIG. 13 —Cross-sectional view of engine with rotor conduit 
         FIG. 14 —Cross-sectional view of engine with double rotor conduits 
         FIG. 15 —Cross-sectional view of eolipile-like engine 
     
    
    
     DRAWINGS—REFERENCE NUMERALS 
     
         
           10 —Turbostirling engine 
           11   a ,  11   b —Engine housing endplates 
           12 —Engine housing body or engine block 
           12   a ,  12   b —Engine housing halves 
           14 —Hot side of housing at heat source 
           16 —Cold side of housing at heat sink 
           18 —Working fluid chamber 
           20 —Working fluid 
           22 —Rotor 
           23   a ,  23   b —Rotor vanes 
           24 —Rotor shaft 
           25   a ,  25   b —Shaft bearing holes 
           26 ,  26   b —Chamber passage, stroke area 
           27   a ,  27   b —Engine housing gasket halves 
           28 ,  28   b —Fluid flux or flow 
           30 —Chamber passage upstream section 
           32 —Chamber passage downstream section 
           34 —Rotor tip concavity 
           36 —Rotor central partition 
           38 —Rotor elbow 
           40 —Rotor proximal opening 
           42 ,  42   b —Rotor peripheral, or distal, opening 
           44 ,  44   b —Rotor shield 
       
    
     DESCRIPTION 
       FIG. 1  shows the basic embodiment of this turbine-action Stirling cycle heat engine. Engine  10  comprises two endplates  11   a  and  11   b  sandwiching a housing  12  including a hot side  14 , a cold side  16 , and a cylindrical chamber  18  containing a working fluid  20  and a rotor  22  including two vanes  23   a  and  23   b  and a shaft  24  rotatably mounted in the housing through bearing holes  25   a  and  25   b  in plates  11   a  and  11   b . Chamber  18  includes an appended cavity, or recessed wall feature, or passage  26  serving as a stroke area for rotary propulsion of rotor  22  by allowing periodic flux of fluid  20 . 
       FIG. 2  shows a detailed view of rotor  22  with vanes  23   a  and  23   b , and shaft  24 . The vanes divide chamber  18  into two hemichambers that are isolated from each other during most of the rotation period of the rotor.  FIG. 3  shows a detailed view of chamber  18  containing fluid  20 . Wall recess  26  forms a bulge in the cylindrical fluid volume. Chamber  18  is topologically isomorphic with a sphere rather than a donut, which is a unique feature of this engine compared to other Stirling engines with a rotary piston/displacer.  FIG. 4  shows engine  10  in its assembled configuration, with plates  11   a  and  11   b  cooperating with engine housing  12  to form an engine block enclosing fluid  20  and rotor  22 , with shaft  24  protruding from the assembly. The midsectional cross-section view of engine  10  will later be shown in  FIG. 7 . The assembly may be held together with bolts or other fastening implements, and bearings may be used to minimize rotational friction, as is known in the art.  FIG. 5  shows an alternate construction of engine  10  in which housing  12  comes in two halves  12   a  and  12   b  separated by gasket halves  27   a  and  27   b , enclosing rotor  22  and the working fluid in an arrangement providing minimal heat loss through body conduction.  FIG. 6  shows the assembled configuration of this alternate embodiment. 
       FIG. 7  shows a horizontal-midplane cross-sectional view of engine  10  with rotor vanes  23   a  and  23   b  far away from stroke area  26 .  FIG. 8  shows a similar view with vane  23   a  starting to engage area  26  and initiating a fluid flow between the hemichambers.  FIG. 9  shows rotor vane  23   a  in full engagement with stroke area  26 , allowing a fluid flow  28  in passageway  26  from the currently hot hemichamber into the currently cold hemichamber, providing an impulse of propulsive stroke on the rotor.  FIG. 10  shows the position of vane  23   a  at the end of the motive stroke, pinching off the fluid flux. The mechanical impulse lasts only for a small fraction of the rotation cycle, when vane  23   a  or  23   b  transit, the stroke zone.  FIG. 11  shows an alternate configuration where stroke zone  26  is slightly offset away from hot wall  14  toward cold wall  16  to compensate for heat transfer delays between the chamber walls and the working fluid. 
     Operation: 
     In normal operation as shown in  FIG. 1 , hot side  14  is brought in thermal contact with a relatively higher-temperature heat source, and cold side  16  contacts a lower-temperature heat sink. A temperature gradient is thus set up across engine housing  12 . Rotor  22  fits with close tolerance in cylindrical chamber  18  and divides its space into two hemichambers filled with working fluid  20 , which can be air or some other gas. As the rotor spins at a steady speed, the fluid contained in each hemichamber is periodically heated and cooled. The temperature vs. time plot exhibits a roughly sinusoidal shape, with a phase difference of 180 degrees between the curves corresponding to the two hemichambers. As any one of the two rotor tips approaches chamber passage  26 , the fluid on the side of its trailing edge is at a higher temperature and pressure than the fluid on the side of its leading edge thanks to ongoing heat exchange with the inner walls of the housing, on both the hot and cold sides. As the rotor tip engages chamber passage  26 , a rheological communication is established between the two hemichambers, and the pressure differential between them induces transient flow  28  of fluid across the passage, imparting an impulse on the rotor and sustaining its continued motion. The total volume of working fluid in the engine remains constant, the pulsatile flow decompressing the fluid in the hotter hemichamber and correspondingly compressing the fluid in the colder hemichamber. As the rotor spins, the same, relatively small, volume of gas pulse is exchanged, back and forth between the two hemichambers on its two sides. A portion of the heat transfer from the source to the sink is accomplished through the cyclical change in the fluid&#39;s state in each hemichamber, and work can be extracted from the rotor as a result. 
     This device can be conceptualized as a closed-turbine, or sealed-turbine, heat engine, where the fluid on each side undergoes an approximate cycle of isochoric heat addition, adiabatic expansion, isochoric heat extraction, and adiabatic compression. While the Otto cycle of an internal combustion engine shares the same thermodynamic constituents, the present device is fundamentally different in that it involves no internal combustion, and no intake and exhaust of working fluid. In that respect, it shares more kinship with a Stirling engine. Moreover, even though the Stirling cycle is idealized as a combination of isochoric and isothermal processes, the PV diagram of a physical Stirling engine is only a coarse approximation of the ideal curve and depends on its construction and type, either alpha, beta, or gamma. For these reasons, the present device may be evocatively referred to as a turbostirling engine. 
     For best performance, the rotor is preferably made of an insulating material and the housing preferably comprises two heat-conductive halves, respectively for the hot and cold sides, joined through an insulating gasket. The working fluid is preferably hermetically sealed inside the chamber at an elevated pressure. Electrical power may be tapped through an internal generator coupled to the rotor, in which case the unit can be hermetically sealed, as in designs advanced by Beale. If mechanical power is to be extracted directly through a shaft extending outside the housing, gas-tight, impermeable bearings would preferably be used. 
     Alternative Embodiments 
       FIG. 12  shows an improved design of the chamber passage and the rotor tip to maximize the impact of the fluid flow on rotor motion. The chamber&#39;s appendiceal cavity  26  which accommodates flow  28  is configured asymmetrically, with an upstream concavity  30  having a smaller radius of curvature and a sharper angle of intersection with the chamber&#39;s cylindrical wall, and a downstream concavity  32  having a larger radius of curvature and a shallower angle of intersection with the chamber&#39;s cylindrical wall. The rotor&#39;s tip is configured with a concavity  34  on the trailing side. These features allow stream  28  to exert a stronger motive force on the rotor tip and a correspondingly stronger counterforce on the housing. Work is thus more efficiently transmitted to the mechanical parts from the motion of the working fluid. Nevertheless, in the cases of both this geometry and the basic scheme shown in  FIG. 1 , on account of the escape of fluid from the hot side to the cold side, an area of lower pressure develops in the hot hemichamber just upstream of flow  28  relative to the average pressure in this hemichamber. Similarly, an area of higher pressure develops in the cold hemichamber just downstream of flow  28  relative to the average pressure in this hemichamber. These localized zones of trailing-edge depressurization and leading-edge pressurization tend to counteract the forward-propelling force of the stream on the rotor, thereby impeding its rotation. 
       FIG. 13  shows a design that helps alleviate the back-pressure problem. Rotor  22  is a hollow structure with an internal conduit, symmetrically divided into two segments by central partition  36 , each segment including an elbow  38 , a centrally positioned proximal opening  40 , a peripherally positioned distal opening  42 , and a shield  44 . When the rotor is engaged with the chamber passage, fluid flows through central opening  40  into the internal conduit and out through peripheral opening  42 . Elbow  38  directs the exiting flow at a near-tangential angle, maximizing the impulse delivered to the rotor. Shield  44  prevents backflow into the hot hemichamber. Depressurization on the hot side now occurs centrally, without adverse effect on the rotor&#39;s motion. 
       FIG. 14  shows a further improvement in which rotor  22  comprises two symmetrical parallel conduits, the proximal opening  40  of each being positioned near the distal opening  42  of the other. In this arrangement, the depressurization in the hot hemichamber becomes a net contributor to the rotor&#39;s motion. 
       FIG. 15  shows a further improvement in which rotor  22  has an internal conduit connecting peripheral openings  42 . The chamber has two symmetrically disposed passages at diametrically opposite locations,  26  and  26   b , supporting an additional motive flow  28   b  at vane  23   b  with opening  42   b  and shield  44   b . The working fluid flows inside the rotor from the hot to the cold hemichambers, symmetrically imparting a rotary impulse at both ends, with motive torque fulcrumed at the axis. This design provides balanced, efficient work delivery. The rotor spins in the same direction if the hot and cold sides are reversed, simplifying the starting requirement. This geometry echoes the configuration of the steam engine invented by Hero of Alexandria two millennia ago, and this device might be called the Stirling eolipile. 
     CONCLUSIONS, RAMIFICATIONS, AND SCOPE 
     The embodiments provide a very simple device which converts a flow of heat into mechanical energy. Although the description above contains many specificities, these should not be construed as limiting the scope of the embodiments but as merely providing illustrations of some of several embodiments. For example, the chamber may be spherical and the rotor may be discoid. Thus, the scope of the embodiments should be determined by the appended claims and their legal equivalents, rather than by the examples given.