Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
  • F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
  • F01B3/04—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis the piston motion being transmitted by curved surfaces
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G1/00—Hot gas positive-displacement engine plants
  • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
  • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
  • F02G1/044—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines having at least two working members, e.g. pistons, delivering power output
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G1/00—Hot gas positive-displacement engine plants
  • F02G1/06—Controlling
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G2244/00—Machines having two pistons
  • F02G2244/02—Single-acting two piston engines
  • F02G2244/06—Single-acting two piston engines of stationary cylinder type
  • F02G2244/12—Single-acting two piston engines of stationary cylinder type having opposed pistons
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G2244/00—Machines having two pistons
  • F02G2244/50—Double acting piston machines

Definitions

• This invention relates to Stirling-cycle engines, also known as regenerative thermal machines, and more particularly to a set of new mechanical arrangements for the construction of a family of multiple-piston, Stirling- cycle machines.
• These machines embody a practical approximation to the well known Stirling thermodynamic cycle; enploy unique design and arrangement of components and materials to achieve an ultimate mechanical simplicity; and perform with high efficiency in the production of both mechanical power (i.e., prime movers, compressors, fluid pumps) and refrigeration (i.e., refrigerators, air conditioners, heat pumps, gas liquefiers).
• a Stirling-cycle engine is a machine which operates on a closed regenerative thermodynamic cycle, with periodic compression and expansion of a gaseous working fluid at different temperature levels, and where the flow is controlled by volume changes in such a way as to produce a net conversion of heat to work, or vice versa.
• the regenerator is a device which in prior art takes the form of a porous mass of metal in an insulated duct. This mass takes up heat from the working fluid during one part of the cycle, and subse- quently returns it to the working fluid prior to the start of the next cycle.
• the regenerator may be thought of as an oscillatory thermodynamic sponge, alternately absorbing and releasing heat with complete reversibility and no loss.
• a reversible process for a thermodynamic system is an ideal process, which once having taken place, can be reversed without causing a change in either the system or its surroundings.
• Regenerative processes are reversible in that they involve reversible heat transfer and storage; their importance derives from the fact that idealized reversible heat transfer is closely approximated by the regenerators of actual machines.
• the Stirling engine is the only practical example of a reversible heat engine which can be operated either as a prime mover or as a heat pump. Background
• the Stirling-cycle engine was first conceived and reduced to practice in Scotland 164 years ago.
• a hot-air closed-cycle prime mover based on the principle was patented by the Reverend Robert Stirling in 1817 as an alternative to the explosively dangerous steam engine. Incredibly, this event occurred early in the Age of Steam, long before the invention of the internal combustion engine and several years before the first formal exposition of the laws of thermodynamics.
• the invention comprises fundamental concepts and mechanical components which are combined to form a new family of Stirling-cycle machines, specifically including the following; (1) a single-acting, two-piston engine having stationary, coaxial, in-line cylinders and employing a pair of cylindrical face cams affixed to the pistons to drive a centrally disposed flywheel element about a hollow shaft, herein termed a "ducted axle", which also serves as the regenerator housing; (2) an engine power level control subsystem associated with that ducted axle machine by which the instantaneous phase angle between the periodic reciprocating motions of the pistons is readily adjusted as a function of power demand; and (3) a quasi double-acting, multiple-piston engine having an annular and parallel array of cylinder and regenerator volumes and employing a single cylindrical drum cam to control the aforesaid instantaneous phase angle and to transfer mechanical work into or out of the machine.
• the primary significance of the present invention is that it represents a radical departure from traditional mechanical arrangements and methods. It thereby achieves a striking reduction in overall complexity and cost, both at the system and at the component level. Indeed, in its simplest and perhaps most useful form, the ducted axle machine, the invention can be functionally accomplished with as few as five moving parts. Yet the same device can be scaled to virtually any size for application to products of enormous diversity, and it can be adapted to run on any fuel, whether gas, liquid, solid, or hybrid, or on any other heat. source, including solar energy.
• the invention constitutes a rare and special combination of superior technical performance, broad market potential, and economic mass producibility, and therefore portends a new era of more thermally efficient and cost effective power products. These include noiseless propane powered lawn mowers, thermal battery powered automobiles, biomass powered fishing vessels, solar powered irrigation pumps, and nuclear powered navy warships. And since the
• Stirling-cycle engine is thermodynamically reversible, the invention will find countless other applications in the realm of refrigerators, heat pumps, air conditioners, and the like.
• a thermal energy storage device thermal energy storage device
• FIG. 1 is an illustration of the operational sequence of events during one complete cycle of an idealized singleacting, two-piston Stirling engine used in the prime mover mode;
• FIG. 2(a) and FIG. 2(b) are schematics which illustrate the idealized pressure-volume and temperature-entropy diagrams of the thermodynamic cycle of the working fluid in the same machine depicted by FIG. 1;
• FIG. 2(c) is a pressure volume diagram which depicts the working of an actual machine;
• FIG. 3 shows a comparison of the basic features of a piston of the ducted axle machine according to my invention (FIG. 3(a)) with a piston of a representative prior art Stirling-cycle machine (Fig. 3(b));
• FIG. 4 is a perspective view which illustrates the overall functional configuration of the ducted axle machine;
• FIG. 5 is a sectional view of the ducted axle machine;
• FIG. 6 is an exploded perspective view of the ducted axle machine;
• FIG. 7 is a partial exploded perspective view of the compression piston and cylinder assembly which illustrates one arrangement for achieving rotation of that assembly about the ducted axle axis relative to the expansion piston and cylinder assembly;
• FIG. 8 illustrates how said rotation alters the relative orientation of the cylindrical face cams on the piston to achieve various output torque levels by adjusting the instantaneous piston phase angle
• FIG. 9 is a schematic representation of the prior art Rinia double-acting, multiple-piston mechanical arrangement
• FIG. 10 is a schematic illustration of how one com pression/expansion/regeneration state of a single-acting, quasi double-acting arrangement according to my invention may be derived from a simple conceptual transformation of such a stage of the Rinia double-acting arrangement;
• FIG. 11 is a schematic representation of a multi-stage, single-acting, quasi double-acting mechanical arrangement according to my invention
• FIG. 12 is a perspective view of the drive assembly and interconnected working volumes of a drum cam machine
• FIG. 13 is an offset sectional view of the drum cam machine of FIG. 12.
• FIG. 14 is a partially exploded perspective view which illustrates the overall functional configuration of the drum cam machine of FIG. 12 and FIG. 13.
• FIG. 1 designates an idealized version of a two-piston, Stirlingcycle prime mover.
• a conceptually constant mass of pressurized gaseous working fluid occupies the working volume between the compression piston 2 and the expansion piston 3.
• the total working volume is comprised by compression space 4, regenerator 5, and expansion space 6.
• a portion of compression space 4 is continually cooled by cooler 7, while a portion of expansion space 6 is continually heated by heater 8.
• Arrows 9 are intended to represent the input of heat by conduction, convection, or radiation. Escape of fluid from the working volume is prevented by the piston seals 10.
• regenerator 5 recovers heat from the working fluid as it is transferred to compression space 4 with the volume remaining constant. The temperature and pressure return to the starting levels of the cycle.
• FIG. 2(a) and FIG. 2(b) wherein the same complete cycle is presented in terras of the pressure-volume diagram and the temperature-entropy diagram for the working fluid.
• the area under a curve on the P-V diagram is a representative measure of the mechanical work added to or removed from the system during the process.
• the area under a curve on a T-S diagram is a measure of the heat transferred to or rejected from the working fluid dur ing the process.
• One favorable er. ⁇ bodiment of the present invention may be characterized as a single-acting, two-piston engine with stationary, coaxial, in-line cylinders and a ducted axle.
• a single-acting, two-piston engine with stationary, coaxial, in-line cylinders and a ducted axle.
• FIG. 3(a) shows the form of a piston 20 of a ducted axle machine as compared to that of a piston 11 from a prior art multiple-piston machine. It may be seen that piston 20 has no connecting rod 14 as does piston 11; that piston 20 incorporates a special cam surface 26 normal to the axis of reciprocation 13; and that there is an axial bore 22 through the top of piston 20. This last condition permits the pistons of a ducted axle machine to be operated in a coaxial arrangment surrounding, and at the opposite ends of, a tubular regenerator/shaft combination.
• the regenerator/shaft or ducted axle 40 serves as the structural backbone of the machine and also provides an internally disposed conduit for the regenerator element 42.
• Ducted axle 40 is coaxial with the machine axis of symmetry 15, extends from one end of the machine to the other between cooler 25 and heater 35, and provides the axle about which the centrally disposed flywheel drive element 45 revolves.
• the rotational motion of the flywheel drive element is guided by a pair of radial bearings 46 and a pair of thrust bearings 43.
• a pair of stationary, coaxial, in-line, right-circular cylinders comprises the housing of the ducted axle machine.
• Compression cylinder 16 encloses compression space 27 and all other compression elements, is closed and sealed at one end by cooler 25, and is threaded to receive cooler heed 29.
• Expansion cylinder 13 encloses expansion space 37 and all other expansion elements, is closed and sealed at one end by heater 35, and is threaded to receive heater head 39.
• heater head 3? may take on a variety of forms to accommodate various combustors, collectors, thermal accumulators, or other sources of heat. Both cylinders (shown in FIG.
• the disk elements are designed to be affixed to the extreme opposite ends of the ducted axle 40 and together with it comprise the interior frame or structural support of the machine.
• Various mechanical fastener means may be used, depending upon whether it is desired to prohibit or permit relative rotation of either disk about ducted axle 40.
• a threaded retainer 41 and a spline 43 are provided; in the second case the retainer 44 is a heavy duty snap ring mated to groove 55.
• the disk elements serve to constrain the longitudinal placement of both cylinders in relation to ducted axle 40 and to direct the flow of working fluid to and from the periphery of cooler 25 and heater 35.
• compression piston 20 incorporates internally a coaxially disposed cylindrical face cam 24 having a cam surface 26 which is oriented in such a way as to face, and to maintain a particular angular position with respect to, the corresponding cam surface 36 of cylindrical face cam 34 similarly fixed within expansion piston 30.
• the pressure forces of the working fluid hold each cam against low-friction cam follower assemblies 56 mounted upon flywheel drive element 45.
• the reciprocating motion of the pistons within the cylinders and along the ducted axle is coupled to and converted into or from rotational motion of flywheel drive element 45, and vice versa, by opposed cam surfaces 26 and 36. Angular rotation of the pistons within the bore is prevented without restricting their axial reciprocation by means of longitudinal slots 50 which are engaged by piston guide assemblies 52.
• Reciprocating seals 21 and 23 prevent the escape of working fluid from compression space 27, while reciprocating seals 31 and 33 similarly contain the working fluid within expansion space 37.
• Rotating seals 49 contain a separate quantity of gaseous buffer fluid within buffer space 47, which is partially pressurized to reduce the magnitude of the static loading on the cams. Holes 51 within flywheel drive element 45 conjoin the compression and expansion sections of buffer space 47.
• working fluid is alternately shifted from compression space 27, over the rounded periphery of compression disk element 28, through the radial flow passages of cooler 25, through regenerator element 42 within ducted axle 40, through the radial flow passages of heater 35, over the rounded periphery of expansion disk element 38, to expansion space 37, and back again,
• Working fluid is introduced into the working volume by means of tank valve 17; buffer fluid is introduced into the buffer space by means of tank valve 19.
• flywheel drive element 45 corresponds to one complete thermodynamic cycle.
• work is done on flywheel drive element 45 to increase its kinetic energy during the aforementioned expansion stroke of each cycle; likewise, work is done on the working fluid by flywheel drive element 45 during the compression and displacement phases of each cycle.
• Net power output may be transferred from flywheel drive element 45 to the indicated output shaft 57 by means of any common mechanical transmission such as a V-belt (designated by numeral 58 in FIG. 4), chain or gear drive assembly. Since the Stirling prime mover is not self-starting, an external starter device (not shown) would normally be an adjunct to the power transmission subsystem.
• a significant consequence of the ducted axle machine arrangement is to permit, in one embodiment of the inven- tion, a uniquely uncomplicated power level control method. It should be recalled at this point that, the instantaneous phase angle between the sinusoidally time-variant reciprocations of the pistons in a Stirling engine is a critical performance parameter. It will be readily appreciated by those skilled in the art that the instantaneous phase angle of the ducted axle machine depends only upon the relative angular displacement of compression cam 24 with respect to that of expansion cam 34 for a given rotational direction of flywheel drive element 45. As shown in FIG.
• the instantaneous phase angle, and consequently the power level of the machine may be either manually or automatically controlled with precision by an enormous variety of mechanical, thermal, electronic, or other conventional and well-known feedback methods.
• this type of power level control one can thereby optimize engine performance and efficiency for any given speed and torque requirements inherent in the nature of the system application.
• speed controlled engines analogous to a synchronous electric motor-generator or converter may be developed on this basis for specialized applications.
• the engine would act either as a prime mover or as a heat pump depending on whether the engine is driving the load or the load is driving the engine at a selected excitation frequency.
• This type of device could have a striking impact on the technology of transportation from the standpoint of total system energy efficiency and conservation.
• the effective utilization of the aforesaid negative torque mode for regenerative braking and reversible heat reclamation in the largely stcp-and-go environment of the automotive prime mover may constitute a technological breakthrough of astonishing economic significance.
• Another favorable embodiment of the invention may be characterized as a single-acting, quasi-double acting, four- piston engine having an annular and parallel array of cylinders and regenerators interconnected in series and incorporating a cylindrical drum cam drive element.
• the machine has four in-line cylinder pairs arranged within and symrr-etrieally about a cylindrical annulus which also contains four regenerator ducts exterior from, parallel to, and alternately interspersed among the cylinders. These are all interconnected in a series so as to form a folded ser pertine arrangement in conjunction with four double-ended pistons within the aforesaid cylindrical annulus.
• the drive shaft is coaxial with and integral to a right-circular cylindrical drum cam mechanism which is interior to and symmetrical with the said annular array of components.
• numeral 61 designates a schematized version of the modern double-acting Stirling engine of the type due to Rinia and described by prior art Patent No. 2,579,702.
• this machine is double-acting because each piston 62 simultaneously works directly against the low temperature working fluid in compression space 64 below, and against the high temperature working fluid in expansion space 66 above, seal 90.
• Each separate working volume so interconnected constitutes a stage wherein both the constant volume displacement functions and the compression ana expansion functions of the Stirling cycle are independently accomplished as long as pistons G2 are constrained by the design cf the drive mechanism (not shown) to move with a suitable phase shift in their displacement.
• the proper phase shift is 90 degrees which is normally accomplished by means of well-known swash plate or crankshaft type drive mechanisms.
• the Rinia arrangement has the advantage that the number of moving parts associated with a given cylinder is only one per cycle, compared with two per cycle in other prior art designs. It also affords a reasonably compact mechanical arrangement when the cylinders are arranged parallel to one another in a cylindrical annulus and the pistons are coordinated by means of a swash plate mechanism internal to the annular volume.
• the drum cam machine represents a fundamental departure from the Rinia arrangement in that the number of cylinders is doubled, and the pistons are incorporated in rigid-body pairs at the opposite ends of double-ended connecting rods in the manner of a dumbbell.
• the desired configuration can be imagined to derive from a simple conceptual transformation of the Rinia arrangement which preserves the manner in which the cylinders, now become disjoint cylinder pairs, are interconnected, but which replaces the double-acting character of the Rinia approach with a single-acting, quasi double-acting mode. It may be seen that the new arrangement disposes of the undesirable aspects of the Rinia arrangement without disturbing the cylic phase relationship inherent in equivalent working volumes.
• numeral 71 designates a schematized version of the quasi double-acting drum cam machine of the present invention.
• this machine is single-acting because only one surface of each piston 72 works directly against working fluid pressure, whether at low temperature in compression space 74 below or at high temperature in expansion space 76 above the seals 90, the other surface being substantially at atmospheric.
• multiple cylinders are fluid flow interconnected, so that the lower compression space 74 o.f one cylinder is connected to the upper expansion space 76 of an adjacent cylinder by means of a flow path past cooler 77, through regenerator 75, and past heater 78 in series.
• a portion of compression space 74 is continually cooled by cooler 77, while a portion of expansion space 76 is continually heated by heater 73;
• arrows 79 are intended to represent the input of heat by conduction, convection, or radiation.
• piston-cylinder pairs can be interconnected in the manner illustrated for four cylinders in FIG. 11, as long as the proper phase shift is maintained between each set. This can be accomplished, as shown in FIG. 12, by taking the drive from sets 82 of paired rotary gudgeon pins located at the mid-point 80 of each double-ended piston connecting rod 81.
• Each gudgeon pin assembly 82 is a low friction cam follower mechanism which is mated in preloaded intiiuate contact with the protruding surfaces of cylindrical drum cam 83 and the linear surfaces of longitudinal cams 91.
• Cylindrical drum cam 83 mechanically converts uniform angular rotation of drive shaft 85, guided by low friction bearings 92 and 92', into simple harmonic reciprocation of each double-ended piston 72 and vice versa.
• the proper phase relationship is kinematically determined by the relative angular position of each piston-cylinder pair about the machine axis of symmetry 15.
• each gudgeon pin assembly 32 consists of pairs of drum cam followers S4 and matching oppositely directed pairs of longitudinal cam followers 86 supported by means of precision low friction needle or roller bearings 37.
• Spring 83 serves to maintain the requisite preloading force, while balls C9 decouple the rotation of drum car., followers 84 from the rotation of longitudinal cam followers 36.
• All longitudinal cam followers 86 are constrained to move back and forth within longitudinal cams 91, which are parallel to both machine axis of symmetry 15 and reciprocation axes 13, and which serve to prevent the relative rotation of pistons 72 within the bore.
• follower axes of rotation 15' are oriented radially with respect to the machine axis of symmetry 15.
• FIG. 14 Attention is now directed to FIG. 14 wherein the overall functional configuration of the drum can machine is illustrated. It should be apparent that all compression spaces 74 are collocated within a single stationary right circular cylindrical "compression block” 94, made of material having comparatively low thermal conductivity. Like wise all expansion spaces 76 are collocated within a single stationary right-circular cylindrical "expansion block” 96 , also made of material having comparatively low thermal conductivity. Compression block 94 and expansion block 96 are conjoined by the four regenerator housings 95 and also by the four longitudinal cams 91.
• a series of shallow segmented annular depressions 93 connect each piston-cylinder working volume with an adjacent regenerator duct 75 and serve as a housing for the internal heat transfer surfaces of either cooler 77 or heater 73.
• Working fluid is conveyed into each piston-cylinder working volume by means of tank valves 99 located on the periphery of compression block 94.
• cooler 77 serves upon assembly and in conjunction with cooler head 97 to close and connect compression volumes 74 with adjacent regenerators 75 and to transfer heat from the internal working fluid to an exterior sink.
• Heater 78 serves upon assembly and in conjunction with heater head 93 to close and connect expansion volumes 76 and with adjacent regenerators 75 and to transfer heat from an exterior source to the internal working fluid.
• the drum cam machine so constructed thereby effects the afor ⁇ said interconnection of stages in a uniquely compact annularly folded serpentine head-to-tail arrangement, clearly illustrated by FIG. 12.
• the drum cam machine design is an arrangement which involves a minimum number of spearate components, and wherein the hot and cold regions of the machine are inherently located at extreme diametrically opposite ends. It should be readily apparent to those skilled in the art that the collocation of cooler elements within a compact cooler head at one end of the drum cam machine, and of heater elements within a similarly compact heater head at the other end of the machine, has the highly desirable effect of reducing heat losses from conduction and radiation to improve the overall thermal efficiency of the machine.
• both compression block 94 and expansion block 96 may new be very conveniently constructed from identical mass-produced precision investment castings. This could be of crucial importance with respect to economical production in a high volur ⁇ e application, by producing an important savings in the cost of materials and labor. A similar economy of production might also be realized for some applications through the design and fabrication of identical cooler head assemblies 97 and heater head assemblies 93. Since the closed cycle Stirling prime mover operates solely on the basis of the difference in temperature in the working fluid between the hot expansion space and the cold compression space, the development of useful power output is not specific to the source of heat available for use.
• the design of the heat source can be any one of a large variety of possible types.
• a rather simple combustion system can be produced, for example, which will cleanly and efficiently burn various kinds of both liquid fuels and gaseous fuels v/ithout any modification whatsoever.
• a single prime mover may be made to operate on regular or premium gasoline, diesel oil, alcohol, crude oil, lubricating oil, olive oil, vegetable oil, propane, butane, natural gas, and synthetic coal gas. It is important at this point to re-emphasize the fact that each small segment of ⁇ well-designed regenerator transfers heat to and from the working fluid with minimal temperature differences. Thus all stages in the regenerator are reversible in an actual thermodynamic sense.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

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• 1982
  • 1982-05-14 WO PCT/US1982/000648 patent/WO1982004098A1/en active IP Right Grant
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  • 1982-05-14 WO PCT/US1982/000649 patent/WO1982004099A1/en active IP Right Grant
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