US3552120A - Stirling cycle type thermal device - Google Patents

Stirling cycle type thermal device Download PDF

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US3552120A
US3552120A US812530A US3552120DA US3552120A US 3552120 A US3552120 A US 3552120A US 812530 A US812530 A US 812530A US 3552120D A US3552120D A US 3552120DA US 3552120 A US3552120 A US 3552120A
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displacer
piston
power
pistons
cylinder
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US812530A
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William T Beale
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Research Corp
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Research Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
    • 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
    • F02G1/0435—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 the engine being of the free piston type
    • 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
    • F02G1/053—Component parts or details
    • F02G1/055—Heaters or coolers
    • 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 an improved Stirling cycle type thermal device, having particular utility as an engine, a refrigerator, and/or a heat pump.
  • Another object of the present invention is to provide such a device having means for controlling the power output or the power input of the device without Varying the mass of gaseous Ifluid involved in the cycle.
  • a further object is to provide such a device including means for providing either power input to the device or power output rom the device through a iiuid pressure cycle and without a mechanical coupling to the power pistons or the piston rod interconnecting the power pistons.
  • a Stirling cycle type thermal device which generally comprises a displacer piston
  • a displacer piston rod connected at one end to said displacer piston and in uid communication at the other end with a second zone
  • said last named means including means for adding heat to or removing heat from each end of the displacer cylinder zone
  • FIG. 1 is a generally schematic view of a dual displacer piston, dual power piston, Stirling cycle type thermal device incorporating the principles of the present invention
  • FIG. 2 is a view similar to that shown in FIG. 1 of a modified form of the present invention illustrating one means for varying the input and output of the device;
  • FIG. 3 is an enlarged fragmentary sectional view of the power input and output varying means
  • FIG; 4 is a view like that shown in FIG. 3 with the mechanism rotated and with portions broken away to more clearly show the operating mechanism;
  • FIG. 5 is a View similar to that shown in FIG. 3 of a modiiied form of power varying means
  • FIG. 6 is an enlarged fragmentary detailed view of one form of regenerator and heat exchanger which may be used with the devices of the present invention
  • FIG. 7 illustrates a modiiied form of power varying means wherein the stroke of the displacer pistons is varied
  • FIG. 8 illustrates a modified form of the present invention wherein hydraulic fluid, in the Work cycle of the engine, is employed as the power limiting means
  • FIG. 9 is a section on line 9-9 of FIG. 8;
  • FIG. 10 is a section on line 10-10 of FIG. 8;
  • FIG. 11 is a diagrammatic view of the hydraulic circuitry connected to the structures shown in FIG. 8;
  • FIG. l2 illustrates a modied form of a combined single displacer piston type engine and linear alternator
  • FIG. 13 illustrates a combination engine and pump constructed in accordance with the teachings of this invention.
  • 10 generally designates a Stirling cycle type thermal device which includes a housing 14.
  • the housing 14 encloses a pair of displacer pistons generally designated D16 and D18.
  • the pistons D16 and D18 are connected for synchronous mtion by a rigid displacer piston rod D20.
  • displacer pistons D16 and D18 are illustrated in an intermediate position between their extreme left and extreme right direction of travel. With this arrangement when, for example, displacer piston D16 is at the extreme left position displacer piston D18 is also at the extreme left position.
  • the pistons D16 and D18 are sized to freely reciprocate in their respective cylinders and since the Stirling cycle is a closed cycle there is no need for piston rings and other sealing means between the cylindrical surfaces of the displaier pistons D16 and D18 and their respective cylindrical walls of the displacer cylinders D22 and D24.
  • the combination heat exchange means and regenerator 26 includes a heater portion 30, a regenerator 32 and a cooler 34 for cylinder D22 3 and corresponding elements 36, 38, and 40 for displacer cylinder D24.
  • the heater 30 communicates with the outer end of cylinder D22 through the opening 42 while the cooler 34 communicates with the opposite end of the cylinder D22 via opening 44.
  • Similar openings 46 and 48 are provided for displacer cylinder D24.
  • the heater section 30 for the regenerator includes a burner 31 connected by conduit 33 to coiled heat exchange pipe 35.
  • the heating medium from the burner 31 leaves the heater section 30 via conduit 37.
  • the regenerator section 32 consists of a plurality of ne copper wires or needles which are relatively densely packed between the heater and the cooler sections 30 and 34.
  • the cooler section consists of a coil 41 similar to heat exchange coil 35.
  • the coil 41 may be supplied with a cooling medium such as water via conduit 43 having a heat exchange coil 45 therein external of the engine and blower means 47 associated therewith.
  • a cooling medium such as water
  • conduit 43 having a heat exchange coil 45 therein external of the engine and blower means 47 associated therewith.
  • a pair of power pistons P60 and P62 are mounted in the housing 14.
  • the power pistons P60 and P62 are interconnected by a power piston rod P64 which rod surrounds corresponding displacer piston rod D20.
  • the power pistons P60 and P62 are interconnected such that when one piston is at the head end of its cylinder the opposite piston is at the inner end of its cylinder.
  • the rod interconnecting the pair of power pistons is not necessary and a uid coupling could be substituted therefor.
  • Each of the power pistons P60 and P62 has a pair of heads 66 and 68 for piston P60 and 70 and 72 for piston P62.
  • Piston heads 66 and 70 communicate with the cool or cold portion of the cylinders D22 and D24 respectively.
  • the heads 66 and 70 are isolated from their opposite heads 68 and 72 by sealing means 74 for piston P60 and 76 for piston P62.
  • the heads 68 and 72 of pistons P60 and P62 are isolated by partition means 78 and O-ring seal 80 whereby a pair of power cylinder spaces 82 and 84 are provided in the device.
  • Power cylinder space 82 is provided with fluid pressure inlet port means 86, outlet port means 88 and cooperating check valves 90 and 92.
  • power cylinder space 84 has inlet port means 94, outlet port means 96, and cooperating check valves 98 and 100.
  • the assembly also includes sealing means 104 between the outer surface of the displacer piston rod D and the inner cylindrical surface of the power piston rod P64.
  • the volume change of the compressed hydrogen decreases the pressure of the CII hydrogen on the right side and increases the pressure on the left-hand side of the device as illustrated in FIG. 1.
  • the pressure is substantially greater on the left and the displacer pistons are driven to the right by the pressure difference acting on the area of sealing means 104.
  • hydrogen gas is moved from the cold region on the left to the hot region on the left, and from the hot region on the right to the cold region on the right.
  • the pressure of the hydrogen on the left-hand side of the device increases, while the pressure of the hydrogen on the right-hand side of the device decreases, thus accelerating displacer piston motion and forcing the power pistons P60 and P62 towards the right to repeat the cycle.
  • the uid in power cylinder chamber 82 is forced out of the outlet conduit 88 via check valve 92 while hydraulic fluid is drawn into cylinder space 84 via check valve 98 and inlet conduit 94.
  • the uid pumped by the power piston may be connected to any suitable pressure fluid type hydraulic motor and the like.
  • the compressed hydrogen in owing from one end of each of the displacer cylinder spaces to the opposite end, passes through the heater, the regenerator and the cooler in one direction of motion, and in the opposite direction passes through the cooler, the regenerator and then the heater.
  • the heater, cooler and regenerator are, as is well known in the art, important features of Stirling cycle thermal devices and without such structures the eticiency of the devices is materially reduced as hereinbefore described.
  • the reference to hydrogen gas as the charging medium is by way of example only and not by way of limitation as any desired fluid medium may be employed in the cycle, as is well known in the art.
  • the double ended device shown in FIG. 1 has an advantage in that it can be easily started in motion by any slight displacement of either power or displacer pistons, if the pumping load is removed from the power piston. This is so since with such a slight displacement, the resulting slight pressure difference would result in motion of the displacer which increases that pressure difference in the manner described above. Thus the device is to a large degree self starting provided only that the high and low temperatures are maintained in the appropriate spaces.
  • the device shown in FIG. 1 were heated on one end only, and started by mechanical energy addition, then it would operate as a heat engine at one end, and a refrigerator at the other.
  • the left hand side were supplied with heating and cooling means, and the right side driven by the left side, then during the rightward motion 0f the pistons, the gas in the space 48 would be compressed, driving thermal energy into the heat exchanger 40, then, when the right side pressure increased to a value greater than the left side pressure, the displacer I would first move left, transposing the gas from space 48 to 46, and from 42 to 44.
  • the power piston moved left the expansion of the gas in space 46 would cool it allowing heat to be removed from the heat exchanger 36.
  • heat exchangers 30 and 36 are hot, while heat exchangers 40 and 34 are cold, thus providing the refrigeration elfect at 40 and 34 with the discharge of heat at 36 and 30.
  • FIGS. 2, 3, and 4 a modified form of the present invention is illustrated.
  • the primary distinction between the form of the invention shown in FIGS. 2, 3, and 4 and that illustrated in FIG. l is that in FIGS. 2, 3, and 4 means are shown for varying the stroke of the displacer pistons and thereby varying the output of the device without altering the volume of the compressed gaseous medium in the displacer cylinders.
  • the housing 14 is discontinuous to provide a space 100 between the two ends of the device.
  • the functions of spacer 78 and of seal 80 in the embodiment shown in FIG. 1 are provided for the embodiment of FIG. 2 by the cylinder end blocks 102 and 104' and by the corresponding seals 106 and 108'.
  • the piston rod P64 for the power pistons P60 and P62 is bored as at 108 to receive a shaft 110.
  • the external end of shaft 110 is provided, in the illustrated form of the invention, with an arm member 114 having a roller 116 at its extended end and the roller 116 is in contact with an adjustable plate or platform 118.
  • the inner end 120 of shaft 110 is provided with a cross arm 122.
  • the extended ends of the cross arm are pivotally connected to linkages 124 and 126.
  • Linkage 124 is in turn pivotally connected to a plunger rod 128 having a stop member 130 on its extended end.
  • Link member 126 is likewise connected to a plunger rod 132 having a stop member 134 at its extended end.
  • the foregoing mechanisms are mounted within a recess 136 within the displacer piston rod D20.
  • the recess 136 is provided with axially extending bores 140 and 142 which receive the plunger rods and stop members.
  • the arm 114 rotates shaft which in turn rotates cross arm 122 to move the stop members and 134 toward or away from the ends 152 and 150 of the bores 140 and 142 in the displacer piston rod D20.
  • variable stop members function as follows: Assuming the displacer piston rod D20 is moving towards the left, in the direction of the directional arrow, and stop members 130 and 134 are positioned as illustrated, the displacer pistons and their piston rod D20 will continue to move left until the surface in the bore 142 strikes the extended end of the stop plate 134. Thereafter, since the shaft 110 passes through a bore 108 in the power piston rod P64', further motion of the displacer piston rod D20' will create a corresponding motion in the power piston rod P64 and the displacer piston assembly will carry the power piston assembly leftwardly with it until the displacer piston assembly reaches the end of its stroke.
  • the volume between the left hand surface of displacer piston D18 and the head 70 of the corresponding power piston P62' will not decrease and correspondingly the space between the right hand end of displacer piston D16 and head 66 of the power piston P60 will not increase once the stop member 134 and surface 150 have come into contact.
  • the pressure of the gaseous medium will not change as greatly as in the case of unrestricted displacer motion, and the power output of the engine will be limited.
  • the opposite stop member 130I will contact the en-d face 152 of bore 140, providing an equivalent power limiting means for the reverse stroke of the engine. It will also be appreciated that by movement of the plate 118 and the control arm 114 the end stop members 130 and 134 may be preset in relationship to their respective end walls 152 and 150 in the bores 140 and 142 in the displacer piston rod D20.
  • FIG. 5 a further means for varying the stroke of the displacer piston is illustrated.
  • the displacer piston rod is designated D20 while the power piston rod is designated P64.
  • 'I'he View illustrated in FIG. 5 is like that shown in FIG. 4 and the elements 102 and 104 comprise cylinder end portions for the power cylinders.
  • the displacer piston rod D20 is recessed in the same manner as illustrated in FIGS. 3 and 4 for piston rod D20'.
  • an adjustable stop mechanism identical in form to that shown in FIGS. 3 and 4, the control mechanism being attached to a control rod 110" which in turn is connected to an actuator rod 114.
  • control rod 110 does not pass through a small bore in the power piston rod P64 as illustrated in FIG. 3. Instead the power piston rod P64 is slotted such that when one of the stop mernbers 130' or 134' engages the end of its corresponding bore the movement of the displacer piston rod D20' is stopped.
  • the stopping action is through the external housing 14 which is bored as at 180 to rotatably receive the control rod 110.
  • This form of the invention need not include a plate member 118 permitting sliding motion between the end of the actuating rod 114' as there is no sliding motion in this form of the invention since the control rod 110 is stationary with respect to the main housing of the engine.
  • the engine 200 generally includes a housing 210, displacer pistons 212 and 214 which displacer pistons are slidably mounted within cylinders formed in the housing 210 and the cylinder spaces may be provided with regenerators such as illustrated in FIG. 6.
  • the apparatus also includes a pair of power pistons 216 and 218 interconnected by a rigid power piston rod 220.
  • Each of the displacer pistons 212 and 214 is provided with a short stublike piston rod 232 and 234 respectively and each of the displacer piston rods 232 and 234 reciprocates in a bore 236 and 238 in the lower pistons 216 and 218 respectively.
  • Bores 236 and 238 are interconnected by a further bore 240 which passes through a portion of each of the power pistons 216 and 218 and centrally through the power piston rod 220.
  • Suitable sealing means isolate the spaces 236 and 238 from the displacer piston spaces 242 and 244.
  • the assembly also includes a stop or limit rod 246 which is freely slidable within the bore 240 and each end of the limit rod 246 is provided with an enlarged end portion generally designated 248 at one end and 250 at the other.
  • the enlarged end portions ride in bores 252 and 254 formed in their respective stub-piston rods 232 and 234 respectively.
  • the power piston working spaces 228 and 230 are suitably connected to conduit means and check valves 260 and 262 and 264 and 266 respectively which conduits and valves control the iiow of pressure fluid into and from the said spaces and the Working uid exiting via conduits and control valves 260 and 264 may be connected to any suitable device to be operated by the system.
  • the working uid within the displacer cylinders is connected to the small bores 236 and 238, via conduits 268 and 2-68, high and low pressure uid accumulators 270 and 272, conduit 274 and check valves 276, 278, 280, and 282.
  • Conduit 274 is connected to one end of a hollow helical spring 284 and the other end 286 of the hollow spring is connected to an internal bore 288 in power piston 216 which internal bore 288 permits the working fluid to ow to both of the bores 236 and 238.
  • the control system also includes valves 290 and 292 in the high and low pressure lines from the high and low pressure accumulators 270 and 272.
  • the displacer pistons 212 and 214 are not connected except by a free-oating limit rod 246 which maintains inner and outer limits on the displacer piston separation and by the gaseous working uid at the inner ends of the displacer pistons stub shafts or rods 232 and 234.
  • the gas maintained at the inner end of each of the stub shafts 232 and 234 can be varied in amount, or volume, by bleeding it out to the low pressure reservoir 272 via valve 290 or by adding a greater quantity from the high pressure reservoir 270 via valve 292.
  • the check valves 276, 278, 280, and 282 maintain maximum cycle pressure in the accumulator 270, and minimum cycle pressure in the accumulator 272.
  • the displacer stroke may be reduced to a minimum allowed by the limit rod 246 by allowing gas to ow out of spaces 236 and 238 through control valve 290 into the low pressure accumulator 272, thus limiting the power output of the machine. If greater power is desired, gas may be admitted to spaces 236 and 238 through valve 292 from the accumulator 270. The displacer stroke may thus be increased by any increment desired until the maximum stroke allowed by the limit rod 246 is reached.
  • displacer pistons when they are not at either maximum or minimum position as determined by the limiter rod, they may move somewhat independently, since the working iiuid in spaces 236 and 238 is elastic, but their overall motion is controlled by the volume of gas in those spaces.
  • FIGS. 8, 9, 10, and 11 A further form of the present invention is illustrated in FIGS. 8, 9, 10, and 11.
  • 300 generally designates an improved Stirling cycle thermal device which includes a housing 310 within which is reciprocally mounted a pair of displacer pistons 312 and 312'.
  • the displacer pistons are associated with conventional regenerator means not shown in these figures.
  • the system also includes a pair of cylindrical power pistons 316 and 318. Each of the power pistons 316 and 318 is centrally bored to permit reciprocation of the displacer piston rod 314 therethrough.
  • Within the housing 310 is a large block element 320.
  • the block is provided with a plurality of bores 322, 322a, and 322b which receive small pistons 324 and 324a and 324b connected to the'inner face of power piston 316.
  • Power piston 318 is also provided with three piston or extensions 326, 326g, and 326b which reciprocate with their piston 318 in bores 328, 328a, and 328b formed in the opposite end of the block 320.
  • the block is further provided with a bore 330 for the displacer piston rod 314 and three small bores 332, 332a, and 332b which interconnect generally dead spaces 334 and 336 between the inner surfaces of the power pistons 316 and 318 and the outer faces of the block 320.
  • each of the small pistons extending from the primary power pistons 316 and 318 are interconnected for cooperative reciprocation by small rods 338, 338:1, and 338b.
  • Each of the six spaces 322, 322a, and 322b and 328, 328a, and 328b are connected to, for example, hydraulic motor 344, FIG. 11, via a pressure fluid control system which permits limiting of the stroke of the power pistons 316 and 318 which in turn restrict the output from the device without bleeding of working fluid.
  • a pressure fluid control system which permits limiting of the stroke of the power pistons 316 and 318 which in turn restrict the output from the device without bleeding of working fluid.
  • the hydraulic control system shown in FIG. 11 will be described as being connected to only spaces 322 and 328, however, as indicated hereinabove all six spaces would be interconnected and operate in unison.
  • Space 322 is connected to a high pressure hydraulic accumulator 346 via conduit 348 and high pressure check valve 350.
  • the space 322 is also connected to cylinder space 352 of controller or shuttle valve means 354.
  • the high pressure accumulator 346 is connected to the hydraulic motor 344.
  • 'Cylinder space 328 is also connected to the high pressure accumulator 346 via conduit 356 and high pressure check valve 358.
  • Cylinder space 328 is also connected to the lower space 360 of shuttle valve means 362.
  • the two shuttle valves 354 and 362 each has a floating piston therein generally designated 364 and 366 respectively.
  • a space 368 which is connected by line 370 to the space 342 in block 320.
  • a further line 372 and check valves 369 and 371 connect line 370 t0 the low pressure hydraulic accumulator 374 and to the high pressure accumulator 346.
  • a line 3718 connects the low pressure accumulator through check valve 380 with line 348.
  • space 382 above floating piston 366 is connected via line 384 to space 340 in block 320.
  • a further line 386 is connected to the high and low pressure accumulator via high and low pressure check valves 388 and 390 while line 356 is also connected to the low pressure accumulator 374 via check valve 392.
  • a portion of the walls of each of the shuttle valve means 354 and 362 comprise bellows-like elements 396 and the device includes a lever arm
  • bellows-like elements 396 of the shuttle valve means 354 and 362 could be replaced by suitable telescopic cylinders of known construction.
  • the power pistons are directly connected to hydraulic pistons 324 and 326, etc., which act in a normal manner in conjunction with inlet and exit flow control check valves and are connected to the high and low pressure accumulators or tanks 346 and 374.
  • the shuttle valve means 354 and 362 act to interconnect the hydraulic pump pistons and the displacer piston rod 314 hydraulically.
  • the displacer pistons must move a proportionate amount in the same direction.
  • This movement of the displacer pistons relative to the hydraulic pump pistons is determined by the ratio of the volume of the spaces 3-40 and 342 to the sum of the displacement of the hydraulic pistons 324 and 326, etc. If it is desired to have the displacer pistons 312 and 312 move three inches for every inch of motion of the power pistons then the diameter of displacer piston rod 314 would equal the diameter of one of the six hydraulic pistons 324, 324a, 324b, 326, 32601, and 326b.
  • the shuttle valve means may be moved by the lever ⁇ 400 to restrict or to increase the motion permitted of the displacer pistons.
  • hydraulic iluid is moved into space 342 and out of space 340 until the left shuttle piston 364 reaches the top of its t cylinder space 368, and the right shuttle piston 366 reaches the lower end of cylinder space 360 at which timefthe flow of hydraulic fluid is restrained by the shuttle valve and the displacer pistons must work against the hydraulic pressure differential in the accumulators in order to continue further movement.
  • FIG. 12 of the drawing there is illustrated an embodiment of the invention wherein the engine consists of a single displacer piston and a single power piston in combination with a linear electric generator.
  • the combined device is generally designated 500 and consists of a displacer piston D518 having one end of a displacer piston rod D520 secured thereto.
  • the piston iD518 is mounted for reciprocation in a cylinder D524 with, for example, conventional clearance between the outer surface of the displacer piston and the bore in the cylinder.
  • the piston P562 in the illustrated form of the invention consists of a permanent magnet having the illustrated poles.
  • the piston is biased into an upper position by a helical spring 528 which bears at its lower end against the lower end 530 of the engine housing 532.
  • the lower end 534 of the rod D520 is also biased by a spring 536 similar to spring 528 hereinabove described. It will also be noted that the lower end 534 of the rod D520 has a peripheral boss thereabout which acts as a limit on the relative axial movement between the power piston and the displacer rod.
  • the displacer piston D518 reciprocates in the cylinder zone 538 which is charged with a predetermined amount of working Huid such as hydrogen.
  • the upper and lower ends of cylinder zone 538 are connected by a gas flow passage which passage may contain a heater 542; regenerator 544 and a gas cooler 546 as is conventional with Stirling cycle type engines.
  • the portion of the engine casing within which the power piston P562 normally reciprocates is surrounded by an iron core 544 and coils 546 and 548 which coils are connected by a suitable electrical conductor 550 and by other electrical conductors 552 and 554 to a load device 556 so that as the magnetic power piston reciprocates an electric voltage is generated in the coils 546 and 548 as is known in the art.
  • the engine is provided with a light weight displacer piston and rod, a relatively heavy piston P562 and heat is applied to the heater 542.
  • the heater increases the temperature at the upper end of the displacer piston, zone 538, and the increasing gas pressure acting on the displacer piston rod area pushes the displacer downwards.
  • the downward moving displacer piston moves the working gas from the cold to the hot space, thus further increasing its pressure relative to the pressure or force of spring 536 and gas below the rod D520, and accelerating the displacer motion downward.
  • the power piston and displacer When the displacer reaches the top of the power piston P562 the power piston and displacer then move downward together until the pressure dilferential between the working spaces and the force of springs 528 and 536 has reversed as a result of the expansion of the working gas and the compression of the springs and of the bounce gas in space 560 and consequently the displacer piston begins to move upward.
  • This upward motion of the displacer piston moves hot gas to the cold space, reducing the working gas pressure and accelerating the motion of the displacer upward.
  • the power piston and displacer piston then move upward together until the increasing working gas pressure forces the displacer down. The cycle then repeats.
  • the ratio of the force of the working fluid/and the mass of the displacer piston must be larger than such force/mass ratio of the power piston, otherwise the power piston will move with or ahead of the displacer, and no pressure differential will be developed.
  • the engine shown in FIG. l2 proved to be self-starting on the application of heat and reliable in operation. It had no internal lubrication except glass-filled Teflon tape on the power piston to provide an easily adjusted diameter for a close fit in the cylinder. There were no piston rings or other seals in the annular gaps of approximately .001 inch around the power piston and displacer rod. Since the engine was adapted to run in a vertical position, there are no side loads except small ones imposed by imperfect spring alignments and asymetrical gas flows.
  • FIG. 13 A further form of engine constructed in accordance with the teachings of the present invention is illustrated in FIG. 13 wherein a combination pump and free piston Stirling engine is shown at 600.
  • the engine consists of a single displacer piston D618 and a single power piston P662 in combination with a pump generally designated 602.
  • the combined device consists of a displacer piston D618 having one end of a displacer piston rod D620 secured thereto.
  • the piston D618 is mounted for reciprocation in a cylinder D624 with, for example, conventional clearance between the outer surface of the displacer piston and the bore in the cylinder.
  • the piston P662 in the illustrated form of the invention consists of a hollow cylindrical member.
  • the power piston is biased into an upper position by a helical spring 628 which bears at its lower end against the lower end 633 of the closed engine housing 632.
  • the lower end 634 of the rod D620 is also biased by a spring 636 similar to spring 628 hereinabove described. It will also be noted that the lower end 634 of the rod D620 has a peripheral boss thereabout which acts as a limit on the relative axial movement between the power piston and the displacer rod.
  • the displacer piston D618 reciprocates in the cylinder zone 638 which is charged with a predetermined amount of working iluid such as hydrogen.
  • the upper and lower ends of cylinder zone 638 are connected by a gas ow passage which passage may contain a heater 642; regenerator 644 and a gas cooler 646 as is conventional with Stirling cycle type engines.
  • conduits 654 and 656 provided with one-way inlet and outlet check valves 658 and 660. Further inlet conduit 656 is connected to a source of liquid to be pumped and outlet conduit 654 is connected to piping as desired.
  • the operation of the free piston engine described with reference to FIG. 13 is such that when the heater increases the temperature of the working Huid in the upper portion 638 of the cylinder D624, the increasing gas pressure acting on the displacer rod area pushes the displacer piston down.
  • the downward moving displacer piston moves the working gas from the cold to the -hot space, thus further increasing its pressure relative to the force of spring 636 and compression of the gas below the displacer rod and accelerating the displacer motion downward.
  • Another useful property of the free cylinder engine of FIG. 13 is that it can produce useful work while at the same time being completely sealed and may be expected to hold its charge of gas for a reasonable time without significant depreciation of performance. Since the enginepump is particularly simple and rugged and the heat engine is capable of self-starting and requires only elementary maintenance to the water pump, it should show promise as a solar powered pump for remote or underdeveloped areas.
  • a Stirling cycle type device comprising a displacer piston, a displacer cylinder zone, said displacer piston mounted for reciprocation in said displacer cylinder zone, a displacer piston rod connected at one end to said displacer piston and in uid communication at the other end with a second Zone, a power piston, a power cylinder, said power piston mounted for reciprocation in the power cylinder normally mechanically independent of the reciprocation of the displacer piston, a working uid in said displacer cylinder zone, means creating a pressure differential between the displacer cylinder Zone and said second zone adapted to act on the area of the piston rod in said second zone, said last named means including means for adding heat to or removing heat from each end of the displacer cylinder zone, means providing a power coupling between the displacer piston and the power piston consisting solely of uid communication conductors between one end of the power cylinder and the displacer cylinder zone.
  • a Stirling cycle type device comprising a displacer piston, a displacer cylinder zone, said displacer piston mounted for reciprocation in said displacer cylinder Zone, a displacer piston rod connected at one end to said displacer piston and in fluid communication at the other end with a second zone, a fluid in said second zone, a power piston, a power cylinder, said power piston mounted for reciprocation in the power cylinder normally mechanically independent of the reciprocation of the displacer piston, a working uid in said displacer cylinder zone, means creating a pressure differential between the displacer cylinder zone and said second zone adapted to act on the area of the piston rod in said second zone, said last named means including means for adding heat to or removing heat from each end of the displacer cylinder zone, means providing a power coupling between the displacer piston and the power piston consisting solely of fluid communication conductors between one end of the power cylinder and the displacer cylinder zone.
  • a Stirling cycle type device comprising a displacer piston, a piston rod adapted to reciprocate with the displacer piston, a cylinder for said displacer piston, an independent cylinder zone for the displacer piston rod, a regenerator for the displacer cylinder through which a gaseous operating medium flows during reciprocation of the displacer piston in its displacer cylinder, a power piston operatively associated with the displacer piston and mechanically free to move independently in respect to the displacer piston, a cylinder for the power piston, means for adding heat to or removing heat from each end of the displacer cylinder and means providing a power coupling and cooperative connective movement between the displacer piston and the power piston, said last means consisting solely of iluid communication conductors between one end of the power cylinder and one end of the displacer cylinder associated therewith and means for removing power from or adding power to the power piston.
  • a Stirling cycle type device comprising a pair of opposed displacer pistons, a rigid rod interconnecting the displacer pistons for synchronous motion of said displacer pistons, a cylinder for each of said displacer pistons, a regenerator for each displacer cylinder through which a gaseous operating medium ows during reciprocation of each displacer piston in its displacer cylinder, a power last means consisting solely of uid communication con- 4 ductors between one end of one power cylinder and one end of the displacer cylinder associated therewith and between one end of the other power cylinder and one end of the displacer cylinder associated with said other power cylinder and means for removing power from or adding power to the power pistons.
  • said last named means comprises a fluid conductor arrangement for directing a hydraulic fluid to and from each power cylinder of each of the power pistons in a zone opposite to the portion of said power cylinders in iiuid communication with the respective ends of their associated displacer cylinders.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Actuator (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US812530A 1969-03-05 1969-03-05 Stirling cycle type thermal device Expired - Lifetime US3552120A (en)

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Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3698182A (en) * 1970-09-16 1972-10-17 Knoeoes Stellan Method and device for hot gas engine or gas refrigeration machine
US3736761A (en) * 1971-08-09 1973-06-05 Philips Corp Cryogenic refrigerator
US3765187A (en) * 1972-08-09 1973-10-16 Us Army Pneumatic stirling cycle cooler with non-contaminating compressor
US3767325A (en) * 1972-06-20 1973-10-23 M Schuman Free piston pump
US3774405A (en) * 1971-09-09 1973-11-27 Us Air Force Magnetically driven cryogen vuilleumier refrigerator
US3782859A (en) * 1971-12-07 1974-01-01 M Schuman Free piston apparatus
US3913339A (en) * 1974-03-04 1975-10-21 Hughes Aircraft Co Reduction in cooldown time for cryogenic refrigerator
US3991585A (en) * 1974-04-29 1976-11-16 U.S. Philips Corporation Cold-gas refrigerator
US4036018A (en) * 1976-02-27 1977-07-19 Beale William T Self-starting, free piston Stirling engine
USRE29518E (en) * 1971-08-02 1978-01-17 United Kingdom Atomic Energy Authority Stirling cycle heat engines
US4090859A (en) * 1977-03-23 1978-05-23 The United States Of America As Represented By The Secretary Of The Army Dual-displacer two-stage split cycle cooler
US4148195A (en) * 1977-12-12 1979-04-10 Joseph Gerstmann Liquid piston heat-actuated heat pump and methods of operating same
US4183214A (en) * 1977-05-05 1980-01-15 Sunpower, Inc. Spring and resonant system for free-piston Stirling engines
US4249378A (en) * 1979-08-31 1981-02-10 Benson Glendon M Thermally actuated heat pump
EP0043249A2 (de) * 1980-06-25 1982-01-06 National Research Development Corporation Nach dem Stirling-Kreisprozess arbeitende Maschine
US4389849A (en) * 1981-10-02 1983-06-28 Beggs James M Administrator Of Stirling cycle cryogenic cooler
FR2523699A1 (fr) * 1982-03-16 1983-09-23 Kryovacs Scient Corp Appareil miniature de refroidissement cryogenique, notamment pour capteurs infrarouges
US4413474A (en) * 1982-07-09 1983-11-08 Moscrip William M Mechanical arrangements for Stirling-cycle, reciprocating thermal machines
US4498298A (en) * 1983-09-15 1985-02-12 Morgan George R Stirling cycle piston engine
US4505119A (en) * 1982-12-09 1985-03-19 Nachman Pundak Flexible linkage for the displacer assembly in cryogenic coolers
JPS60101249A (ja) * 1983-11-07 1985-06-05 Matsushita Electric Ind Co Ltd スタ−リング機関
US4543793A (en) * 1983-08-31 1985-10-01 Helix Technology Corporation Electronic control of cryogenic refrigerators
WO1986006439A1 (en) * 1985-04-22 1986-11-06 Stig G. Carlqvist Motor Consultant (C.M.C.) Aktieb Method and arrangement in heat engines
US5022229A (en) * 1990-02-23 1991-06-11 Mechanical Technology Incorporated Stirling free piston cryocoolers
US5142872A (en) * 1990-04-26 1992-09-01 Forma Scientific, Inc. Laboratory freezer appliance
US5329768A (en) * 1991-06-18 1994-07-19 Gordon A. Wilkins, Trustee Magnoelectric resonance engine
EP0778452A1 (de) * 1995-12-08 1997-06-11 Cryotechnologies Stirling-Kühlanlage mit Drehantrieb
FR2819555A1 (fr) * 2001-01-17 2002-07-19 Conservatoire Nat Arts Groupe electrogene a mouvement lineaire alternatif a base de moteur stirling, et procede mis en oeuvre dans ce groupe electrogene
US20040040297A1 (en) * 2000-06-06 2004-03-04 Sander Pels Stirling motor and heat pump
US20070210659A1 (en) * 2006-03-07 2007-09-13 Long Johnny D Radial magnetic cam
WO2007110184A2 (de) * 2006-03-23 2007-10-04 Josef Gail Heissgasmaschine
EP1877710A1 (de) * 2005-04-21 2008-01-16 Industrial Research Limited Druckwellengenerator
US20100287954A1 (en) * 2009-03-25 2010-11-18 Jayden Harman Supersonic Cooling System
WO2010147461A1 (en) 2009-06-18 2010-12-23 Enatec Micro-Cogen B.V. Amplitude stabilizer for a stirling engine signal generator
US20110030390A1 (en) * 2009-04-02 2011-02-10 Serguei Charamko Vortex Tube
US20110048048A1 (en) * 2009-03-25 2011-03-03 Thomas Gielda Personal Cooling System
US20110048062A1 (en) * 2009-03-25 2011-03-03 Thomas Gielda Portable Cooling Unit
US20110051549A1 (en) * 2009-07-25 2011-03-03 Kristian Debus Nucleation Ring for a Central Insert
US20110048066A1 (en) * 2009-03-25 2011-03-03 Thomas Gielda Battery Cooling
US20110113792A1 (en) * 2009-09-04 2011-05-19 Jayden David Harman Heat Exchange and Cooling Systems
JP2011226392A (ja) * 2010-04-20 2011-11-10 Alpha Plus Power Inc 熱機関
US20130180238A1 (en) * 2012-01-13 2013-07-18 Sunpower, Inc. Beta Free Piston Stirling Engine In Free Casing Configuration Having Power Output Controlled By Controlling Casing Amplitude Of Reciprocation
WO2013087600A3 (de) * 2011-12-12 2013-08-08 Erich Kumpf Thermische einrichtung zum erzeugen von mechanischer und/oder elektrischer energie
CN103925106A (zh) * 2014-04-30 2014-07-16 郭远军 一种负压动力机器及其做功方法
US8820114B2 (en) 2009-03-25 2014-09-02 Pax Scientific, Inc. Cooling of heat intensive systems
US20170115036A1 (en) * 2015-10-23 2017-04-27 Sumitomo Heavy Industries, Ltd. Gm cryocooler
CN106813412A (zh) * 2015-10-23 2017-06-09 住友重机械工业株式会社 Gm制冷机
US10598125B1 (en) 2019-05-21 2020-03-24 General Electric Company Engine apparatus and method for operation
US10711733B1 (en) 2019-05-21 2020-07-14 General Electric Company Closed cycle engine with bottoming-cycle system
US10724470B1 (en) 2019-05-21 2020-07-28 General Electric Company System and apparatus for energy conversion
US10830174B1 (en) 2019-05-21 2020-11-10 General Electric Company Monolithic heat-exchanger bodies
US20220123627A1 (en) * 2021-03-12 2022-04-21 Harbin Engineering University Free Piston Generator Based on Rigid Synchronous Transmission System
US11371754B2 (en) * 2016-06-02 2022-06-28 Sumitomo Heavy Industries, Ltd. GM cryocooler
US12078066B1 (en) 2023-06-26 2024-09-03 Hyliion Holdings Corp Pressure control system for a closed-cycle engine

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GB1397548A (en) * 1971-08-02 1975-06-11 Atomic Energy Authority Uk Stirling cycle heat engines
ZA753251B (en) * 1974-06-07 1976-04-28 Research Corp Power piston actuated displacer piston driving means for free-piston stirling cycle type engine
DE2820526C2 (de) * 1978-05-11 1982-04-22 Schneider, Christian, Dipl.-Ing., 8650 Kulmbach Heißgas-Hubkolbenmotor mit elektromagnetisch angetriebenem Verdränger
CH660779A5 (de) * 1983-06-20 1987-06-15 Sulzer Ag Kaeltemaschine oder waermepumpe mit thermoakustischen antriebs- und arbeitsteilen.
US5873246A (en) * 1996-12-04 1999-02-23 Sunpower, Inc. Centering system for free piston machine
DE10034377C1 (de) * 2000-07-14 2001-08-23 Hubert Stierhof Wärmekraft- oder Kältemaschine mit freiem Verdränger, bewegtem Zylinder und feststehendem Kolben

Cited By (95)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3698182A (en) * 1970-09-16 1972-10-17 Knoeoes Stellan Method and device for hot gas engine or gas refrigeration machine
USRE29518E (en) * 1971-08-02 1978-01-17 United Kingdom Atomic Energy Authority Stirling cycle heat engines
US3736761A (en) * 1971-08-09 1973-06-05 Philips Corp Cryogenic refrigerator
US3774405A (en) * 1971-09-09 1973-11-27 Us Air Force Magnetically driven cryogen vuilleumier refrigerator
US3782859A (en) * 1971-12-07 1974-01-01 M Schuman Free piston apparatus
US3767325A (en) * 1972-06-20 1973-10-23 M Schuman Free piston pump
US3765187A (en) * 1972-08-09 1973-10-16 Us Army Pneumatic stirling cycle cooler with non-contaminating compressor
US3913339A (en) * 1974-03-04 1975-10-21 Hughes Aircraft Co Reduction in cooldown time for cryogenic refrigerator
US3991585A (en) * 1974-04-29 1976-11-16 U.S. Philips Corporation Cold-gas refrigerator
US4036018A (en) * 1976-02-27 1977-07-19 Beale William T Self-starting, free piston Stirling engine
US4090859A (en) * 1977-03-23 1978-05-23 The United States Of America As Represented By The Secretary Of The Army Dual-displacer two-stage split cycle cooler
US4183214A (en) * 1977-05-05 1980-01-15 Sunpower, Inc. Spring and resonant system for free-piston Stirling engines
US4148195A (en) * 1977-12-12 1979-04-10 Joseph Gerstmann Liquid piston heat-actuated heat pump and methods of operating same
US4249378A (en) * 1979-08-31 1981-02-10 Benson Glendon M Thermally actuated heat pump
EP0043249A2 (de) * 1980-06-25 1982-01-06 National Research Development Corporation Nach dem Stirling-Kreisprozess arbeitende Maschine
EP0043249A3 (en) * 1980-06-25 1982-07-14 National Research Development Corporation Improvements in or relating to stirling cycle machines
US4389849A (en) * 1981-10-02 1983-06-28 Beggs James M Administrator Of Stirling cycle cryogenic cooler
FR2523699A1 (fr) * 1982-03-16 1983-09-23 Kryovacs Scient Corp Appareil miniature de refroidissement cryogenique, notamment pour capteurs infrarouges
US4413474A (en) * 1982-07-09 1983-11-08 Moscrip William M Mechanical arrangements for Stirling-cycle, reciprocating thermal machines
US4505119A (en) * 1982-12-09 1985-03-19 Nachman Pundak Flexible linkage for the displacer assembly in cryogenic coolers
US4543793A (en) * 1983-08-31 1985-10-01 Helix Technology Corporation Electronic control of cryogenic refrigerators
US4498298A (en) * 1983-09-15 1985-02-12 Morgan George R Stirling cycle piston engine
JPS60101249A (ja) * 1983-11-07 1985-06-05 Matsushita Electric Ind Co Ltd スタ−リング機関
JPH0375746B2 (de) * 1983-11-07 1991-12-03 Matsushita Electric Ind Co Ltd
WO1986006439A1 (en) * 1985-04-22 1986-11-06 Stig G. Carlqvist Motor Consultant (C.M.C.) Aktieb Method and arrangement in heat engines
US4815291A (en) * 1985-04-22 1989-03-28 Stig G. Carlqvist Motor Consultant (C.M.C.) Method and arrangement in heat engines
US5022229A (en) * 1990-02-23 1991-06-11 Mechanical Technology Incorporated Stirling free piston cryocoolers
WO1991013297A1 (en) * 1990-02-23 1991-09-05 Mechanical Technology Incorporated Stirling free piston cryocoolers
US5142872A (en) * 1990-04-26 1992-09-01 Forma Scientific, Inc. Laboratory freezer appliance
US5329768A (en) * 1991-06-18 1994-07-19 Gordon A. Wilkins, Trustee Magnoelectric resonance engine
EP0778452A1 (de) * 1995-12-08 1997-06-11 Cryotechnologies Stirling-Kühlanlage mit Drehantrieb
FR2742215A1 (fr) * 1995-12-08 1997-06-13 Cryotechnologies Refroidisseur stirling a pilotage rotatif
US20040040297A1 (en) * 2000-06-06 2004-03-04 Sander Pels Stirling motor and heat pump
US6877314B2 (en) * 2000-06-06 2005-04-12 Sander Pels Stirling motor and heat pump
US20050072148A1 (en) * 2001-01-17 2005-04-07 Pierre Francois Power unit with reciprocating linear movement based on stirling motor, and method used in said power plant
WO2002057612A1 (fr) * 2001-01-17 2002-07-25 Conservatoire National Des Arts Et Metiers (Cnam) Groupe electrogene a mouvement lineaire alternatif a base de moteur stirling, et procede mis en oeuvre dans ce groupe electrogene
US7152404B2 (en) 2001-01-17 2006-12-26 Conservatoire National Des Arts Et Metiers (Cnam) Power unit with reciprocating linear movement based on stirling motor, and method used in said power plant
FR2819555A1 (fr) * 2001-01-17 2002-07-19 Conservatoire Nat Arts Groupe electrogene a mouvement lineaire alternatif a base de moteur stirling, et procede mis en oeuvre dans ce groupe electrogene
EP1877710A4 (de) * 2005-04-21 2010-12-15 Ind Res Ltd Druckwellengenerator
US8171742B2 (en) 2005-04-21 2012-05-08 Industrial Research Limited Pressure wave generator
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US20080253910A1 (en) * 2005-04-21 2008-10-16 Alan James Caughley Pressure Wave Generator
US20070210659A1 (en) * 2006-03-07 2007-09-13 Long Johnny D Radial magnetic cam
WO2007110184A3 (de) * 2006-03-23 2008-08-21 Josef Gail Heissgasmaschine
WO2007110184A2 (de) * 2006-03-23 2007-10-04 Josef Gail Heissgasmaschine
US20100287954A1 (en) * 2009-03-25 2010-11-18 Jayden Harman Supersonic Cooling System
US8820114B2 (en) 2009-03-25 2014-09-02 Pax Scientific, Inc. Cooling of heat intensive systems
US20110048048A1 (en) * 2009-03-25 2011-03-03 Thomas Gielda Personal Cooling System
US20110048062A1 (en) * 2009-03-25 2011-03-03 Thomas Gielda Portable Cooling Unit
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US20110048066A1 (en) * 2009-03-25 2011-03-03 Thomas Gielda Battery Cooling
US20110088878A1 (en) * 2009-03-25 2011-04-21 Jayden Harman Supersonic Cooling System
US20110094249A1 (en) * 2009-03-25 2011-04-28 Jayden Harman Pressure Shock-Induced Cooling Cycle
US8353169B2 (en) 2009-03-25 2013-01-15 Pax Scientific, Inc. Supersonic cooling system
US8353168B2 (en) 2009-03-25 2013-01-15 Pax Scientific, Inc. Thermodynamic cycle for cooling a working fluid
US8333080B2 (en) 2009-03-25 2012-12-18 Pax Scientific, Inc. Supersonic cooling system
US20110030390A1 (en) * 2009-04-02 2011-02-10 Serguei Charamko Vortex Tube
WO2010147461A1 (en) 2009-06-18 2010-12-23 Enatec Micro-Cogen B.V. Amplitude stabilizer for a stirling engine signal generator
US20110051549A1 (en) * 2009-07-25 2011-03-03 Kristian Debus Nucleation Ring for a Central Insert
US8887525B2 (en) 2009-09-04 2014-11-18 Pax Scientific, Inc. Heat exchange and cooling systems
US20110139405A1 (en) * 2009-09-04 2011-06-16 Jayden David Harman System and method for heat transfer
US20110113792A1 (en) * 2009-09-04 2011-05-19 Jayden David Harman Heat Exchange and Cooling Systems
US8359872B2 (en) 2009-09-04 2013-01-29 Pax Scientific, Inc. Heating and cooling of working fluids
US8365540B2 (en) 2009-09-04 2013-02-05 Pax Scientific, Inc. System and method for heat transfer
JP2011226392A (ja) * 2010-04-20 2011-11-10 Alpha Plus Power Inc 熱機関
WO2013087600A3 (de) * 2011-12-12 2013-08-08 Erich Kumpf Thermische einrichtung zum erzeugen von mechanischer und/oder elektrischer energie
US20130180238A1 (en) * 2012-01-13 2013-07-18 Sunpower, Inc. Beta Free Piston Stirling Engine In Free Casing Configuration Having Power Output Controlled By Controlling Casing Amplitude Of Reciprocation
CN103925106A (zh) * 2014-04-30 2014-07-16 郭远军 一种负压动力机器及其做功方法
CN103925106B (zh) * 2014-04-30 2015-03-11 郭远军 一种负压动力机器及其做功方法
US20170115036A1 (en) * 2015-10-23 2017-04-27 Sumitomo Heavy Industries, Ltd. Gm cryocooler
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DE1933159A1 (de) 1970-12-10

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