EP1017933A1 - Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique - Google Patents

Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique

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Publication number
EP1017933A1
EP1017933A1 EP98955343A EP98955343A EP1017933A1 EP 1017933 A1 EP1017933 A1 EP 1017933A1 EP 98955343 A EP98955343 A EP 98955343A EP 98955343 A EP98955343 A EP 98955343A EP 1017933 A1 EP1017933 A1 EP 1017933A1
Authority
EP
European Patent Office
Prior art keywords
transfer
entropy according
volume
working
entropy
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP98955343A
Other languages
German (de)
English (en)
Other versions
EP1017933B1 (fr
Inventor
Thomas Ertle
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SOLISOLAR ENERGY GMBH
Original Assignee
Thomas Ertle
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE1997142660 external-priority patent/DE19742660A1/de
Application filed by Thomas Ertle filed Critical Thomas Ertle
Publication of EP1017933A1 publication Critical patent/EP1017933A1/fr
Application granted granted Critical
Publication of EP1017933B1 publication Critical patent/EP1017933B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • 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
    • F02G1/02—Hot gas positive-displacement engine plants of open-cycle 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
    • F02G2270/00—Constructional features
    • F02G2270/70—Liquid pistons

Definitions

  • thermodynamical energy such as when using solar energy or heat sources, e.g. the combustion of biomass, waste heat or geothermal energy, for a needs-based local supply for pump power, mechanical drive, electrical energy, heat supply, refrigeration, cleaning or separation, chemical or physical change of at least one substance through the coupling with a periodic thermodynamic
  • An integrable energy storage can be as low as possible.
  • thermodynamic cycle processes (Stirling engine, steam turbine) are each coupled to two heating baths with a constant temperature.
  • energy can only be transported optically (with parabolic mirrors or light guides) or via a material flow with a phase transition (heat pipe).
  • thermal energy can only be stored in chemical stores or in
  • the invention is based on the central object in a method and / or in a device for transferring entropy such as the use of solar energy or heat sources, such as the combustion of biomass, waste heat or geothermal energy, for the needs-based local supply for pump power, mechanical Drive, electrical energy, heat supply, kite generation, cleaning or separation, chemical or physical change of at least one substance by coupling with a periodically running thermodynamic cycle, the efficiency of which is as high as possible, to achieve that the necessary expenditure of energy carriers or mechanical energy as well as constructive, technological, economic or ecological effort for • the construction of the entire device or the operational sequence of the entire process,
  • regenerator such as a (foldable) membrane, folded, telescopic or resilient sheets, a shape-changeable regenerator structure or one
  • ERSATZBLA ⁇ (RULE 26 delimit at least one partial volume with a minimal size largely without overlap with the comparable and in some cases induce movements by elements of the control system that act on it, by means of which the ratio of this partial volume to this working volume is either increased or decreased in the time periods of the periodically running thermodynamic cycle, during which this working volume is only changed in size to a smaller extent and depending on the pressure of the working fluid in this working volume at least one specific valve whose opening and closing time decisively influences the thermodynamic cycle and which can delimit this working volume against at least one external space which fills up is un fluctuating with at least one working medium with partially different fluctuations in this working volume relative to the periodic pressure change during these time periods pressure, the control system or the flow pressure is predominantly kept open (in the time periods characterized above) and flows through, which (valves) is kept closed during other time periods running between these time periods, in which the pressure of the working fluid in this working volume by the shift of the above or other components or components by the control system and the resulting change in the average temperature of the working fluid in
  • Working volume through the mechanical compression device either increases or decreases and the ratio of each sub-volume as defined above to this working volume is changed only to a significantly lesser extent, whereby during a time interval that is much longer in relation to the period, either a thermal energy intake or release of at least one substance of a continuous or periodic swelling and declining mass flow takes place at a sliding temperature or at several temperature levels and in this working volume at least one working medium acts at least partially as a working fluid which goes through the periodic thermodynamic cycle.
  • the method according to the invention runs in a device according to the invention for
  • Compression device e.g. one or more pistons, liquid pistons or membranes, and optionally at least one liquid interface or no at least one working volume filled with working fluid is largely limited, in which • in each case at least two separable from the working fluid in one
  • Working volume through the mechanical compression device either increases or decreases and the ratio of each sub-volume as defined above to this working volume is changed only to a significantly lesser extent, whereby during a time interval that is much longer in relation to the period, either a thermal energy intake or release of at least one substance of a continuous or periodic swelling and declining mass flow takes place at a sliding temperature or at several temperature levels and in this working volume at least one working medium acts at least partially as a working fluid which goes through the periodic thermodynamic cycle.
  • the entire cyclic process in a working volume can be assigned several circular processes running in parallel between two heat reservoirs with constant temperatures, viewed with reasonable idealization.
  • Each heat reservoir of these cyclic processes can be assigned to a partial volume of the working volume which is filled with working fluid and as defined above.
  • At least one substance of a continuous or periodically increasing and decreasing mass flow is heated or cooled either by the absorption or release of thermal energy at a lower temperature difference relative to the overall temperature change when it comes into contact with the hotter or colder heat reservoirs of these cycle processes, the phase or can transform chemical composition.
  • At least one substance of a continuous or periodically swelling and declining mass flow is supplied with thermal energy at a sliding temperature or at several temperature levels.
  • the principles can change due to the temperature change over a large temperature interval
  • the thermal energy can be very effective and inexpensive with a sensitive memory that has a large surface such as a gravel fill, can be exchanged when working fluid flows through.
  • the heat energy transport can be achieved by moving a capacitive working medium, e.g. Air.
  • thermal energy when a gas mixture is vaporized, thermal energy must be supplied over a temperature interval or at several temperatures.
  • the preamble and the main claim of the patent cited in sections include a restriction to regenerative work or heating machines, in which the work volume available to the working fluid is increased by a flowing through, rigidly connected structure of regenerator, cooler and heater as in the known Stirling engines is divided into only two periodically changeable partial volumes.
  • the working gas runs through a cycle between two heat reservoirs, from which thermal energy is taken or supplied at constant temperatures.
  • thermal energy that is taken from the machine above Tk can only have been transported through irreversibility and must come from the heater, since there is no relevant cycle in the machine, the thermal energy from the temperature level of the coldest part volume of the gas-filled working volume to the higher temperature level pumps.
  • the mechanical work supplied (used) or given (won) during a period of the entire cycle to balance the energy balance is largely directly transferred from a storage space when at least a certain amount of at least one fluid substance is transferred moved to another storage space with different pressure.
  • the cited patent is compared to the more abstract formulation of the task chosen above. limited to cooling or heating a heating or cooling medium through thermal contact with heat exchangers of a regenerative work or heat engine.
  • Fresh air can flow into the working volume through one of the valves at atmospheric pressure, which can result in decisive synergy effects in some applications.
  • hot air is taken up in a working volume and blown out as cooler air into a room with higher pressure, some of the heat energy released when the air is cooled being taken up by the cooler.
  • hot fresh air at atmospheric pressure from exhaust gases
  • Temperature interval (eg 200 ° C to 500 ° C) can be used to achieve a higher final temperature of the working fluid when heated in the collector's absorber with relatively little effort.
  • the device shown in FIG. 1 can work, inter alia, as a thermal gas compressor (with the integrated effect as an engine) and, owing to the simple structure and the relatively simple theoretical description of the cycle, forms a good starting point for understanding the more complex machines which are also based on the principle of the invention, Devices or procedures construction
  • a working volume filled with gas as working fluid is largely enclosed by a working cylinder as pressure housing 1, a slidingly sealed piston 2.
  • a frame 6 is slidably sealed against the cylinder wall 5, on which a heat exchanger 7 and a regenerator 8 which is unchangeable in structure or size are mounted so that the gas must flow through them
  • a pressure tank 20 is connected to the pipe system at 13 in front of the fan (turbine) 14.
  • the piston 2 and the frame 6 are moved periodically by hydraulic pistons 21, 22, 23 as is characterized in FIG. 4, FIG. 5, FIG. 6 or the subsequent description of the cycle.
  • the drive tube 24 of the frame 6 is guided by the piston 2 in the stroke direction through seals from the working volume.
  • this drive pipe two pipes for the cooling water run and are sealed against the inner wall of the drive pipe in such a way that no gas exchange which interferes with the cycle can take place between the working volume and the environment.
  • Movable hoses 25, 26 connect these pipes to fixed connections 27, 28 of a cooled water reservoir. so that the cooling water can circulate in a closed circuit.
  • the liquid in the heat exchanger 7 should always have a lower pressure than the working volume, so that no liquid is pressed into the working volume, which could lead to dangerous sudden steam development, but the liquid in the heat exchanger is displaced by the inflowing working fluid.
  • the hot gas to be cooled is introduced directly into the piping system of the entropy transfer device (see FIG. 1) and removed again at 15, then the losses and the design outlay of the heat exchanger 18 can be eliminated.
  • the hydraulic pistons 21, 22 and 23 exchange mechanical power via a controlled valve system 29 of the control system via a hydraulic pump 30 with a flywheel 31 and a component 32 acting as an electric motor and / or generator.
  • Working fluid can be exchanged from the part of the pipeline system 19 to the flow channel 12 by a valve 33, optionally driven by a fan 34 or not by a further valve 35
  • the valve 33 remains closed for the time being
  • the sequence of movements is determined by the control system and is rough and sufficient for the following analysis in Fig.4, Fig.5, Fig.6 I.
  • the regenerator system 11 has a temperature profile in the equilibrium operating state, the mean temperature T of which is significantly above the cooler temperature T k , results from this directly the time course of the mean temperature in the working volume T m (t) and is shown qualitatively in Fig. 4, Fig. 5, Fig. 6 II.
  • the pressure P 0 in the part of the piping system 19 before the inlet valves corresponds to atmospheric pressure.
  • the fan 14 is intended to work in such a way that the pressure Pi in the space 13 of the pipeline system adjacent to the outlet valve 4 is only slight relative to the pressure difference
  • valves 3 and 4 are opened or closed by the (flow) pressure of the gas. With the corresponding reduction in the work volume from V a to V b by the
  • This work W from _ corresponds to a hatched area in FIG.
  • the coolest partial volume becomes smaller with a constant working volume due to a displacement of the frame 6 with cooler 7 and regenerator 8, which leads to an increase in the average temperature of the gas in the working volume.
  • this valve is opened and the expansion of the gas associated with the rise in the mean temperature causes a gas quantity of the mass m A flows out of the working volume through the outlet valve, is expanded adiabatically in the fan 14 and thereby does the work W nu tz, which corresponds to an area in FIG.
  • V ⁇ V t by a corresponding, possibly very small division, such that for V; without an effective
  • I h B i ⁇ ⁇ B Boltzmann constant; T; : Temperature in V; ; ⁇ ; Number of gas molecules in
  • N - * i [-m ⁇ - d 3 r
  • the gas should not flow relative to the heat transfer surfaces which are necessary for the thermodynamic cycle. Since the gas in the entire working volume is in direct contact with heat transfer surfaces in this period of time to large heat capacities, which are necessary for the thermodynamic cycle and due to their special movement, the gas is not moved relative to it, this period of the cycle can be described by an isothermal expansion the same formulas apply to the exchanged thermal energy or work as for the time period abc
  • the largely homogeneous regenerator structure 1 1 fills the entire working volume with a very large heat capacity that is assumed to be infinite in the following, and this as infinite
  • the working volume is divided by E - 1 planes arranged perpendicular to the stroke into E partial volumes of equal size. Due to the symmetry, the temperature is ideally constant on these planes.
  • the heat energy Q, 1 / E * Q e f g is withdrawn from the regenerator structure 11 in each of these partial volumes by the isothermal expansion of the gas, ie [l; E].
  • the regenerator structure 11 is removed by the Cooling of the hot gas quantity of the mass m A flowing in through the inlet valves 3 effectively supplies energy at each period, since as a result a larger amount of gas flows from the hot part into the colder part of the regenerator structure 11 than in the reverse flow direction.
  • the jth of these partial volumes is (see above) through the isothermal levels of the
  • Flow channel 12 flows from the part of the piping system 15.
  • the fan 34 can stop.
  • Mass m A of the gas which is sucked in hot and pressed at a lower temperature and pressure to umIH.
  • T l5 PP 0 remains unchanged, the same amount of thermal energy is supplied to the regenerator system 11 only during a period when the exchanged gas quantity is cooled more intensely. In this way, a larger temperature difference T] - T 2 can be achieved with the same pressure ratio Pi / Po.
  • the temperature T 2 can be stabilized relatively easily by a simple thermostat control for the inlet valve 35.
  • the inlet valve 35 is only opened when the gas (15) exceeds the specified temperature (even).
  • This greater thermal energy is partially withdrawn from the regenerator system 1 1 in the time period efg during the effectively isothermal expansion of the gas from Pi to P 0 , a larger pressure ratio Pi / Pn being able to be achieved and thus a total of D ⁇ O period more energy being implemented, the on the regenerator 8 or on the regenerator system 1 1, the total heat energy exchanged and the associated thermal losses can be increased in a much lower ratio.
  • the mass flow through the adjustable fan can be set in 3 stages (off, medium, large) and the large stage is always switched on when a temperature falls below a certain temperature, then the temperature T can be sufficient with a value with relatively little effort be stabilized.
  • the device shown in FIG. 1 can also be operated as a refrigerator, which cools a quantity of gas over a large temperature interval,
  • the then driven fan (turbine) 14 must press the gas from the part of the piping system 19 with the pressure P 0 into the part 13 with Pi.
  • the direction of flow of the gas is reversed (everywhere in the working volume), the structure of the device and the movement sequence remain as shown in Fig.l or Fig.4, Fig.5, Fig.6.
  • the exhaust valve 4 becomes an intake valve in that, with the stop direction unchanged in the time period c-d-e, e.g. is held open against the flow pressure by an attacking spring connected to the control system.
  • the gas then flowing in with the pressure Pi releases thermal energy to the regenerator system 11 during cooling.
  • Thermal energy is withdrawn from the regenerator system during the time period efg during the effectively isothermal expansion of the gas (as at the front in the gas compressor; engines) from Pi to P 0 .
  • the front shown in the description of the engine is cde even when the refrigeration machine through the interaction of the partial processes in the time periods and efg a linear in the stroke direction temperature field T (r) formed in the regenerator 1 1, the mean temperature T m in the Refrigeration machine is below the cooler temperature T k (development over time of T m (t) in Fig. 4, Fig. 5, Fig. 6: replace max. T m (t) by min. T (t).
  • the intake valves of the engine 3 can act as exhaust valves in the refrigeration machine if, with the stop direction unchanged, g-h-a e.g. by an attacking spring connected to the control system against the
  • Heat exchanger 18 that comes from the cooling of the other gas stream
  • the mean temperature of the gas in the working volume is reduced by the expansion of the regenerator system 11 at a constant working volume, which is due to the valve 4 being kept open at a constant pressure P ! for an inflow of warmer gas, an additional supply of thermal energy to the
  • the device shown in FIG. 1 and already described as a motor machine can, as already largely shown at the front, also be operated as a refrigeration machine.
  • a greater temperature difference in the amount of gas of the mass m A taken up and given off by the working volume can be achieved if, in the period gha, a gas amount of the mass mH by in this case with the same stop as an exhaust valve acting valve 35 flows into the space 15, which is kept open gha by the control system against the flow pressure in this time period.
  • air is also pushed into the working volume by the turbine 14 and the valve 4.
  • T 1; Pi Po is supplied to the regenerator system 11 during a period of equal heat energy only when the gas is cooled more.
  • a larger temperature difference Ti - T can be achieved with the same pressure ratio P ⁇ / P O.
  • the temperature T 2 can be stabilized relatively easily by a simple thermostat control for the outlet valve 35.
  • the outlet valve 35 is only opened when the gas at 19 exceeds the specified temperature (even). Reaching a smaller temperature difference T t - T 2 when using the device characterized in Fig.l as a refrigerator
  • the engine shown in FIG. 1 can, as already shown above, also be operated as a refrigerator. If, as in the case of the engine, a larger pressure difference P - Po is also to be used for the cooling machine for a certain cooling, then this can be achieved if, in the time period gha, the gas quantity of the mass m B is passed through a further (controlled) inlet valve 35 into the Flow channel 12 is blown from the room 15 with a fan 34. As a result, the regenerator system 11 is supplied with a correspondingly greater thermal energy in comparison to operation without the valve 35 and, in the case of isothermal expansion in the time period efg, an appropriately greater thermal energy is extracted again by expansion with a larger pressure ratio Pi Po.
  • the advantages of these measures or the regulation of the temperature T 2 are largely analogous to those of the correspondingly operated engine in FIG. 1
  • Valves of the gas from P 0 to Pi of the regenerator system 11 are supplied with thermal energy.
  • the open valve 4 from the turbine causes gas temperature T H from
  • the gas is expanded to the pressure Po when the valves are closed, and thermal energy at the temperature T is thus removed from the heat exchanger.
  • the average temperature in the working volume is increased with the expansion of the regenerator system 1 1 and at Po is by the
  • regenerators in the working volume act as filters.
  • the heat energy supplied to the fresh air partly comes from a colder heat reservoir such as the ambient air or the groundwater.
  • the sketched heat pump can be constructed in such a way that the air practically does not come into contact with lubricants and the filters can be easily replaced if they are dirty.
  • Valves must be used to regulate the amount of gas flowing into the working volume.
  • valves 4 and 35 or corresponding valves adjoin each of these flow channels, through which the temperature intervals for the exchanged
  • Gas quantities can be varied over wide ranges (see Fig. 1b, 1 c).
  • this entropy transformer may be easier to set up, since no heat exchanger (e.g. car cooler) is necessary.
  • this construction can also be operated in such a way that lukewarm gas with higher pressure is pressed into the working volume by a turbine and thereby the flow direction but not the periodic sequence of movements (see Fig. 4, Fig. 5, Fig. 6) is changed and hot and cold gas flow out of the working volume at a lower pressure.
  • the gas may by a Entropietransformator 2 working volumes under the cooling water temperature T k are cooled.
  • the driven fan 14 is replaced by one of the devices described above with the effect of a gas compressor, the hot gas being absorbed by the working volume which can be assigned to the gas compressor and, at higher pressure, by the outlet valve 4 this working volume is delivered into a room of the piping system, to which a buffering pressure vessel can be connected and from where the gas, after a previous cooling to approx. T k, flows through the valve 4 acting as an inlet valve into the working volume, which the refrigerating machine can be assigned.
  • the gas cooled under T flows out of this working volume through the valves 3 and possibly 35.
  • the periodic flow through the valves 35 of the two working volumes can be set accordingly.
  • the buffering pressure vessel can be dimensioned smaller or can be omitted.
  • a hot and cold gas quantity is absorbed by a first working volume as described above and released again as a cool gas quantity at higher pressure and absorbed by a second working volume, which it releases again as a warm gas quantity at the outlet pressure.
  • the liquid from a heat exchanger or an additional amount of gas was cooled in the second working volume.
  • regenerators 36, 37, 38, 39 act on the working volume of FIG. 8, FIG. 9 or FIG other regenerators 40 and 41 each have four tubes attached, each part of one of the four concentric arrangements of tubes 42 of the control system.
  • These components 36 - 41 as well as the frame with the heat exchanger 43 acting as a cooler are sealed with V2A sealing brushes on bronze cylinder wall plates 44 as well as the pipes for the heat exchanger liquid 45, 46 so that they are at minimal (less than 10%) ) Leakage flow between the seal and the cylinder wall can be flowed through.
  • regenerators are made of a lower V2A perforated plate with as little metal surface as possible, with U-profiles made of V2A welded on for reinforcement and open parallel to the perforated plate, in which metal fibers are sheathed with V2A fabric (wire diameter approx. 0.1 mm) (center of gravity of the diameter at 40 micrometers ) are inserted, which are clamped and enclosed by another perforated plate.
  • the two perforated sheets are held together by a wire winding where the perforated sheets have been deformed in such a way that the outer surfaces of these regenerators have no local elevation despite the wire winding.
  • the perforated plate merges into a plate without holes, whereby the seals are held and sealed to the metal fibers so that they flow through.
  • FIG. 6 a working volume filled with gas as the working fluid is largely enclosed by a pressure housing 47, inlet 48 and outlet valves 49.
  • the gas can flow through the inlet valves from a space of the piping system corresponding to FIG. 1 in FIG. 1 into the partial volume between the cylinder cover and the regenerator 36 and from a space between the regenerators 39 and 40 through
  • Flowing out pipe 50 in which a pipe 45 with the line 46 for the heat exchanger liquid runs concentrically and in a fixed connection and which periodically enters sealed into one of the pipes 51 with brushes 52, which does not periodically move and which limits the working volume.
  • the gas can pass through the outlet valves 49 into a space of the gas piping system which corresponds to 13 in FIG.
  • these elements are guided in the stroke direction in the middle of the working cylinder on a fixed tube.
  • Each two adjacent tubes of the tube arrangements 42 have a greater difference in length than stroke (see FIG. 9 T), the tube having a smaller diameter being longer.
  • the tubes movably connected at one end to the regenerators 36 - 40 by the carriage 53 are connected at the other end to two levers 56, each of which is opposite the other relative to the tube axis, for bearings 55, which are movably connected at the other end, each with two Pipe arrangement 42 with respect to lever 57 opposite the pipe axis, on which the point of engagement 58 for the movable connection is at a uniform distance from the pipe axis, the larger the pipe diameter is.
  • the tube connected at one end to the regenerator 41, which is inside the tube arrangement 42, is connected at the other end to a short piece of tube 60 via two rods 59 guided past the levers of the other tubes, which is on the tube attached to the regenerator 36 can slide and are also movably connected to the lever 56 described above, which are connected to the lever 57 at the other end with the greatest distance from the pipe axis.
  • the entire moving structure of 55-60 is enclosed so tightly in the operating state by a housing 61 that as little dead space as possible remains, since within this housing, which is connected to the working volume, the pressure is changed periodically, i.e. this housing is part of the pressure vessel. Since the flow area of the heat exchanger when using car coolers and the space required for the frame supporting it is significantly smaller than the area in the working volume perpendicular to the stroke, the movement sequence shown in Fig. 9 T was chosen, with no regenerator at the time period abc Heat exchanger structure 43 is present and, above all, the gas flows through the car cooler.
  • the regenerators 40 and 41 lie close to the heat exchanger structure, the large-volume interstices of which are filled with wood (or GRP) so that the flow through the regenerators is as uniform as possible.
  • the gas flowing past the car cooler has to overcome a significantly greater flow resistance than that flowing through an car cooler, so that gas flows through the car cooler in the time period a-b-c with only a small bypass gas flow.
  • the displaceable carriage 53 is connected to the frame of the heat exchanger structure 43 at fixed intervals with screws and spacer tubes (118) which are guided through the carriage of the regenerator 40.
  • the pipes 45 within which the lines 46 for the heat exchanger liquid are arranged, are also connected to this frame. These tubes are guided through tubes 62, which also form part of the pressure housing, and seals 63 out of the working volume and connected to a frame 64. Two rigidly attached to this frame in the stroke direction, with respect to the
  • the center axis of the working volume, in the stroke direction, arranged opposite pipes 65 are guided in the stroke direction by two slide bushes 66, which are fastened to a parallel pipe 67, which is firmly connected to the pressure housing.
  • Tension springs 68 which are stretched between the upper ends of the fixed tube 67 and the lower end of the tube 65 attached to the moving frame 64, partially compensate for the weight of the moving structure.
  • two connecting rods 69 are fastened so that the bearings are arranged opposite one another in the stroke direction with respect to the central axis of the working volume.
  • the other ends of these connecting rods 69 are each fastened to chains 70 with a bearing axis parallel to the chain bolts.
  • the bearing attached to the chain 70 is formed by two identical disks 71 with two bores 72 each, the disks 71 engaging in the bore 73 of the connecting rod 69 from both sides, enclosing the connecting rod 69 by their collar 74 and with the bolts of the chain lock 75 of a triple chain attached to the double chain 70 and incorporated into it.
  • One of the chains 70 runs over two sprockets 76 supported on one side so that the parallel bearing axes are arranged perpendicular to and with a symmetry of displacement in the stroke direction and the connecting rod does not abut when the chain rotates.
  • a further sprocket 77 with an adjustable relative angle is fastened on the same axis, which is coupled via a further chain 78 to a sprocket 79, which is connected to one of two uniaxially mounted double sprockets 80 on an axis with an adjustable relative phase, over which a triple roller chain 81 runs so that it protrudes over the sprocket in the direction of the chain pin on the side on which no axis leads to the sprocket.
  • the pitch radii of the sprockets 77 and 79, and 80 and 76 are each the same size, the chains 81 and 70 are of the same length.
  • a chain link with rollers is removed from the roller chain and a lever 82 is inserted between two sheets 83 from the chain, each with two holes, together with a simply drilled disc 84 through two chain locks (plug-in links with spring locks) 85 and further chain links 86 where due to the protrusion of the chain, there is no contact with the sprockets.
  • another lever 87 is rotatably attached at one end in the same way and cranked so that the other end is supported on a bearing 88 between the ends of the other lever 82 and the connecting rod, which ends on the same axis 89 rotatably fastened
  • the distance between the bearing axes of the levers 87, 82 corresponds to the pitch circle radius of the double sprockets (79 sprockets) or 76.
  • the connecting rod 89 is rotatably mounted on another frame 90 at the other end.
  • Four tubes 91 extending in the stroke direction are fastened to the frame 90, and these are inserted through seals 92 into tubes which belong to the pressure housing and are connected at the other ends to the carriages 53 of the uppermost regenerator 36.
  • the axes of the lower sprockets 76 with respect to the central axis of the working volume in the stroke direction are so long that there is sufficient space to attach a further sprocket 94 to the other end, which is connected to a sprocket 97 by a chain 95, 96 guided above it which is attached to an axis that forms part of the electric geared motor (which is equipped with an additional flywheel on the motor axis.
  • a chain is guided by 2 deflection chain rollers 98 so that the chain wheels 97 and 94 engage in the links of the chain 95 from different sides.
  • the distances between the bearings of the levers 82,87 can be selected appropriately, and the chains stretched accordingly and adjusted by adjusting the phase of the sprockets 77 and 76 or 79 and 80, which are attached to an axle
  • the entire chain bearing also largely has a mirror symmetry with respect to the direction of rotation with respect to the plane in which the central axis lies in the stroke direction of the working volume and is parallel to the bearing axes of the chain wheels.
  • This movement is characterized in that in a time period abc of the cycle the regenerators 36 - 40 largely lie against each other and are flowed through by part of the gas in the working volume from the cooler
  • the conduit 46 penetrates the attachment of the tube 45 to the lower lifting frame 90, is sealed there against the tube 45 and fastened by a screw running in a spacer tube there so that it can be inserted into the tube 45 by about 10 cm the short connecting hose can be installed from the pipe to the Auto-Kuhler socket.
  • a pipe sleeve 99 is pushed over the end of the working volume, on which the seals 100 of the regenerator 40 slide and on the small metal parts 101 are welded with holes in the stroke direction, through which it is screwed to the air guide tube 50 with welded nuts (120)
  • the pipe piece 45 and the tubular sleeve 99 are screwed in the radial direction with a metal piece (11), to which the frame which carries the heat exchanger is screwed.
  • the pipe pieces 45, 46 can be fitted with seals from the outside into the pressure vessel 63 can be inserted
  • the periodically moving rigid piping system for the heat exchanger liquid of a heat exchanger has two pipes 102, 103 running in the direction of flow before and after the heat exchanger, each of which extends into the stroke of a separate standing vessel 104, 105 with heat exchanger liquid from above, a pump 106 being used for the heat exchanger liquid pumps from the heat exchanger in the working volume into the vessel 105, from where they flow into another vessel 104 after the heat has been given off in another stationary heat exchanger (e.g. cooled by groundwater).
  • the liquid level of these vessels with an opening should, unlike in FIG.
  • a thin hose (garden hose) is inserted into the tube 102 from the vessel 104 to the lowest point of the heat exchanger in the working volume.
  • the thermal expansion of the material becomes a problem with the desired size (100 liters working volume) of the machine This is countered by the fact that the pressure vessel 47 itself largely remains at ambient temperature and is insulated from the hot interior (for example with glass foam 107) to fill the space
  • the cylinder wall 44 in the stroke direction is then formed from two layers of staggered sheet metal strips with a width of 20-30 cm, the approx. 3-5 mm wide joints running in the stroke direction.
  • the surfaces of the pressure housing arranged largely perpendicular to the stroke direction are also e.g. largely insulated with glass foam 107 to fill the interior, which is held by a reinforced flat sheet.
  • this sheet must be generously cut out in the direction of its center of area and have a corresponding distance from the border at the edge.
  • Valves 48 and / or 49 are opened or kept open via a Bowden cable or linkage by a lever which is pressed with a roller onto control plates which are attached to the chain links of chains 70 or 81.
  • a parallel valve with a significantly smaller cross-sectional area is opened beforehand by the same control to reduce the pressure difference.
  • grating planes 108 to be flowed through by the gas and arranged perpendicular to the stroke direction are characterized by the control system as in FIG. 91 so that they move to this regenerator 41 or the neighboring one , already moving the grating level either maintain a certain distance (e.g. 20% of the total stroke) or remain as close as possible to the boundary surface of the pressure vessel, for driving the grating levels 109 in the partial volume of the working volume, which is only delimited by the regenerator 36, the same largely applies .
  • the work volume shown in Fig.8 becomes like the work volume in Fig.1 on
  • Spacer tubes 118 which are guided through the carriage of the regenerator 40 are connected to the frame of the heat exchanger structure 43 at fixed intervals.
  • the pipe section 45 and the pipe sleeve 99 are screwed in the radial direction with a metal piece 119, to which the frame is screwed, which carries the heat exchanger.
  • regenerators 36 - 40 have a temperature profile in the equilibrium operating state, the middle one
  • Temperature T mg is significantly above the temperature T of the cooler.
  • the inlet and outlet valves should be connected to the surrounding systems, ie, due to the reserve space 17, the pressure P 0 corresponds to that
  • the turbine 14 in FIG. 1 is intended to work in such a way that the pressure Pi is changed only slightly relative to the pressure difference Pi-Po by the interaction with an upstream compensating pressure vessel in the space of the pipeline system adjacent to the outlet valve 13.
  • the valves 49 and 48 are opened and / or closed by the (flow) pressure of the gas.
  • the gas In the equilibrium operating state, the gas has its lowest mean temperature T m (t) in the working volume cf. Fig.9 I reached at time a. Immediately afterwards, the inlet valve is closed by the flow pressure from the working volume due to the increase in the average gas temperature T m im
  • the compressed gas emits thermal energy to the cooler.
  • the gas in the working volume has reached the highest average temperature T m (t).
  • the outlet valve is closed again by the pressure in the working volume which is lower than that of Pi.
  • the pressure in the working volume is still too great for the inlet valves to open, so that the reduction in T m (t) leads to a reduction in the pressure P (t) in the working volume.
  • the regenerators 37-40 absorb heat energy (see Q e f g ) since the gas flowing through is expanded again between two regenerators.
  • the outlet valve is opened by the somewhat higher pressure in the working volume and a gas quantity of mass m A flows out. At time e, the maximum average temperature of the gas in the working volume has been reached.
  • Time j a the smallest value for T m (t) is reached again.
  • the amount of gas flowing in is given off by the transfer of thermal energy to the
  • Regenerators 36 - 40 and cooled when mixed with cooler gas.
  • a partial volume divided from the working volume by the components characterized in claim 1 is deprived of thermal energy during a full period if, on average, it is (significantly) smaller during the time period of the pressure increase than during that of the pressure decrease
  • This partial cycle process drives a second partial cycle process, which pumps from the partial volume of the working volume, which is only delimited by regenerator 41, into the partial volume, which is only delimited from the working volume by regenerator 36
  • a valve that is controlled by the temperature of the endangered partial volume can prevent this process from being started unintentionally by a sticking valve and can lead to destruction due to overheating, which valve causes a constant pressure in the working volume in an emergency. If the outlet valve is opened by a correspondingly lower selection of the pressure Pi already a small fraction of the time period abc after the point in time a at which the lowest average gas temperature prevails in the working volume, the pressure in the working volume is increased in this cycle process, if the partial volume delimited only by regenerator 41 and the part volume adjacent to the cooler largely the maximum and that delimited only by regenerator 36
  • Partial volume and the partial volumes between two regenerators largely have their minimum size.
  • the pressure Pi can be chosen such that no heat energy is removed or supplied on average per period to the partial volume of the working volume which is only delimited by the regenerator 36.
  • the movement sequence characterized in FIG. 10 has the advantage that the
  • Regenerators are covered or better trained. In contrast to the representations in FIG. 8, the lower lifting frame 90 must be connected to the lowest regenerator 41.
  • the pressure PI can be set so that an analog one for the corresponding partial volumes
  • the partial volumes of the working volume between two of the regenerators 36-40 are reduced by the fact that the gas flowing through is further expanded in the time period efg between two regenerators. These partial volumes are supplied with thermal energy during a period by virtue of the fact that due to the gas quantity of the mass m A which is hotly taken up into the working volume by the inlet valve 48 and which is released cooler through the outlet valves 49, the regenerators 36-39 flow through the hottest side with one around them Gas quantity of mass m A larger gas volume is flowed through than from the cooler side.
  • Regenerators a temperature profile with a larger gradient in the flow direction.
  • one of the partial volumes defined above is supplied with more thermal energy than is extracted by the periodic flow.
  • One of the valves 49 in FIG. 8 can be used like the valve 35 in FIG. 1 in order to achieve the described changes in the temperature differences when cooling or heating a portion of the exchanged gas at the same ratio of the pressures Pi / Po.
  • a fan for drawing in hot air is not absolutely necessary, since hot air is sucked into the working volume as soon as the regenerator is in motion.
  • regenerator 40 moves away from the inlet valve 48, hot air is drawn in, cold air is blown out and the regenerators 36-39 are heated.
  • the flow resistance of the regenerator acts.
  • P x can be selected so that the total amount of gas drawn in remains constant, ie this measure reduces the
  • T l5 P 1; P 0 is the same amount of heat energy supplied to the regenerators 36 to 39 only during a period when the exchanged amount of gas is cooled more.
  • a larger temperature difference Ti - T 2 can be achieved with the same pressure ratio Pi / Po.
  • the temperature T 2 can be stabilized relatively easily by a simple thermostat control for the valve 49 corresponding to the inlet valve 35 in FIG.
  • the inlet valve 35 is only opened when the gas (15) exceeds the specified temperature (even).
  • the mass flow through the adjustable fan can be set in 3 steps (off, medium, large (and the step large is always switched on by a thermostat when the temperature falls below a certain temperature, the temperature T 2 can thus be sufficient with a relatively low effort Value should be stabilized.
  • a fan for drawing in hot air is not absolutely necessary in order to make the arrangement described work as a gas compressor, since in the
  • the system described above which acts as a motor machine and has the working volume shown in FIG. 8, can, after a few changes, also be operated as a refrigeration machine which cools a gas quantity over a large temperature interval.
  • the then driven fan (turbine) 14 must remove the gas from the part of the
  • Control system against the flow pressure is kept open.
  • the gas then flowing in with the pressure Pi releases thermal energy to the regenerators 36 to 39 during cooling.
  • Thermal energy is extracted from these regenerators during the subsequent time period g-f-e by the expansion of the gas between two regenerators (cf. front: engines).
  • a linearly stepped temperature field T (r) is formed in the regenerators 36 to 39, whose average temperature T m at the Chiller is below the cooler temperature T k .
  • T m (t) corresponds to reversing the chronological sequence and replacing max. T m (t) by min. T m (t) of the qualitative representation in FIG. 9 II.
  • the average temperature of the gas in the working volume is increased when the regenerators 36 to 39 are pushed together in the subsequent time period edc.
  • the inlet valve 48 of the engine in FIG. 8 acts as an outlet valve in the refrigerator if it is kept open against the flow pressure by the control system during this period of time edc with the stop direction unchanged and Gas, among other things, due to the increase in the mean temperature in constant
  • Refrigeration machine (see. Figl) is introduced and removed again at 15, the losses and the design effort of the heat exchanger 18 can be omitted.
  • the average temperature of the gas in the subsequent time period c-b-a the average temperature of the gas in
  • the partial volume of the working volume which is divided only by the regenerator 36, is (additionally) removed from thermal energy by opening the valve 48 or a valve with a smaller cross-sectional area acting in parallel to it before the pressure difference is completely equalized.
  • the partial volume of the working volume which is only delimited by regenerator 41, is supplied with thermal energy by opening a valve acting in parallel with one of the valves 49 before the pressure difference is completely equalized.
  • a greater temperature difference in the amount of gas of the mass m A taken up and given off by the working volume can be achieved if, in the time period edc, a gas amount of the mass m H is in this case relative to Fig.8 modified stop as an outlet valve as valve 35 in Fig.1 acting valve 49 flows into space 15, which is kept open edc by the control system against the flow pressure in this time period.
  • regenerators 36 to 39 are only supplied with the same amount of thermal energy during a period if the gas is cooled to a greater extent.
  • a larger temperature difference Ti - T 2 can be achieved with the same pressure ratio Pi / Po.
  • the temperature T can be stabilized by a simple thermostat control.
  • the outlet valve 49 corresponding to FIG. 1 valve 35 is only opened when the gas at 15 exceeds (just) the specified temperature.
  • the system described in FIG. 1 with the effect of a gas compressor can, as already shown above with reference to FIG. 1, also be operated as a refrigeration machine if the working volume and parts of the control system are exchanged for the arrangement shown in FIG. As with the engine, it should also be used with the chiller for less cooling with a certain one Pressure difference Pi - P 0 are worked, this can be achieved if, in the time period edc, the gas quantity of the mass m B through a further (controlled) valve 49 corresponding to the inlet valve 35 between the regenerators 39 and 40 with a fan from the room 15 is blown.
  • Fig.8 working volume is integrated, act as a heat pump when the control system, the regenerators 36 to 41 with unchanged periodic
  • Movement sequence drives and the direction of work
  • Turbine 14 maintains the pressure increase due to an opening of a valve through which gas flows in, with the pressure drop due to an opening of a valve through which gas flows out, is interchanged.
  • Partial volume of the working volume is cooled. Compared to the refrigeration machine described above, the time course of the mean temperature T m (t) and the pressure P (t) against the stroke H (t) is half
  • the pressure of the gas in the working volume is increased to the maximum value due to the rise in the average temperature of the gas when the valves are closed by the displacement of the regenerators 36-41. Due to the adiabatic compression of the gas flowing through the partial volumes between two of the regenerators 36 to 39, thermal energy is supplied to these regenerators.
  • the gas in the partial volume adjacent to the cooler is expanded adiabatically and thereby cooled Tn of the time period cba, the average temperature in Working volume increased with the displacement at a constant distance between the regenerators 36 to 39, the cooled gas flows through the heat exchanger and takes thermal energy at the temperature T k and at Po 48 gas of the temperature Ti is given off in the time period ahg since the mean temperature T mg (t) of the gas in the working volume is increased.
  • regenerators in the working volume act as filters and can be easily replaced if they are dirty.
  • the heat energy supplied to the fresh air partly comes from a colder heat reservoir such as the ambient air or the groundwater.
  • the sketched heat pump can be constructed in such a way that the air practically does not come into contact with lubricants and the filters can be easily replaced if they are dirty.
  • the gas is removed from the partial volume of the working volume between regenerators 36 and 37.
  • the construction required for this is comparable with that for the gas exchange into or out of the partial volume between the regenerators 39 and 40. 50 used, which is attached to the regenerator 36 and slidably sealed against the pressure housing in a connected tube 206 (see FIG. 51), from which the air is exchanged by valves. Water in the pressure vessel
  • Heat exchanger structure of the cooler 43 is limited.
  • These tubes are movably connected to one another by a lever construction such as 57, 58.
  • the regenerator 41 is omitted, the valve 48 remains unchanged.
  • the air guide pipe 50 also points in the other direction and slidably plunges into a pipe corresponding to 51, which is connected to the pressure vessel in a sealed manner, the 49 corresponding outlet valve being able to be attached to the pressure vessel.
  • Regenerators are attached (ideally: at times as far apart as possible), two tensioned belts are attached, one of which is wound up while rotating a shaft that is sealed out of the pressure vessel while the other is being unwound.
  • each regenerator is driven by two shafts and the
  • the pressure housing is filled with water to such an extent that the cooler structure 43 is largely completely immersed in its lowest position
  • the pipe 50 also serves as an overflow for the water level in the pressure housing.
  • Overflowing W ater r is from the gas in a in the piping system downstream of the valve
  • the water from this pressure tank is fed through a pipe through a, with a
  • actuated valve Float through the water level in this pressure tank, actuated valve is closable, returned to the pressure vessel around the working volume.
  • the water level in the pressure vessel can be changed periodically (by actuating a compression device) and an (additional) pressure change can be achieved in this way.
  • regenerators 36 to 40 For the flow through the regenerators 36 to 40 can also be achieved in that a sheet metal is sealingly attached to the edge of each of these regenerators, which is always immersed in the water even in the periodic operating state. In order to minimize the losses due to the heat transfer surface, this sheet must be provided with a water-repellent surface with a low thermal conductivity.
  • regenerator 41 is omitted and the heat exchanger 43 is replaced by the regenerator 207.
  • the regenerators 39 and 207 are accordingly connected to each other at a fixed distance and the regenerator 40 is temporarily applied.
  • regenerator 208 which is temporarily present at the regenerator 207 with the regenerator 38 which is temporarily present at the regenerator 39, the regenerator 209 temporarily at the regenerator 208 with the regenerator 37 temporarily at the regenerator 38 and the temporarily at the regenerator 209 becomes analogous
  • Regenerator 210 is fixedly connected to the regenerator 36, which is temporarily applied to the regenerator 37.
  • the air exchange through the air guide tubes 205 and 211 takes place predominantly simultaneously, as does the air exchange through the air guide tubes 50 and 212.
  • One of the valves 49 or one of the valves 213 through which the air flows out of or into the air guide tube 212 becomes like this when the stop direction changes Valve 35 used in Fig.l.
  • Valves must be used to regulate the amount of gas flowing into the working volume in order to maintain a certain temperature difference during cooling or heating of the periodically exchanged amounts of gas. If the cooler gas is to experience only a minor change in temperature, gas is sucked out of the working volume as described above during its inflow process through a valve 49 acting like valve 35 with a fan. Since the gas from two different partial volumes, which are separated from one another by a regenerator 40, can flow out of the working volume through different valves 49 and 213 into different spaces of the piping system, (together with a valve which acts like valve 35), the two
  • Temperature changes occurring temperature differences can be varied over a wide range.
  • Heat exchanger e.g. car cooler
  • a system that acts as a gas compressor can also act as a heat pump or refrigerator with minor changes.
  • This construction can also be operated in such a way that lukewarm gas with a higher pressure is periodically pressed into the working volume by a turbine and hot and cold gas periodically flow out of the working volume at a lower pressure.
  • both the cycle shown at the front of the heat pump and the one at the chiller can be used.
  • the respective temperature differences can additionally with a valve that like that
  • Valve 35 acts to be adjusted
  • gas can be cooled below the cooling water temperature T by an entropy transformer with 2 working volumes
  • the driven fan 14 is replaced by an engine described above, the hot gas being absorbed by the working volume that can be assigned to the engine and at higher pressure through the outlet valve 49 or 4 into a space of the piping system is delivered, to which a buffering pressure vessel can be connected and from where the gas, after a previous cooling to approx. T, flows through the valve 49 acting as an inlet valve into the working volume, which can be assigned to the refrigerator.
  • This working volume flows under Tt cooled gas through the valves 48 and possibly the valve 49 acting like valve 35
  • the periodic flow through these valves of the two working volumes can be set accordingly, if the movements shown in FIG. 4, FIG. 5, FIG. 6T occur simultaneously in a working volume, the buffering pressure vessel can be smaller be dimensioned, or omitted
  • This combination can also be used as a heat pump to heat a liquid
  • a hot and cold gas volume is taken up from a first working volume as described above and then released again as a cool gas amount at higher pressure and taken up by a second working volume that it releases again as a warm gas amount at the outlet pressure.
  • the liquid of a heat exchanger was used in the second working volume or cooled an additional amount of gas
  • Pressure housing 110, the valves 111, 112 and the slidingly sealed piston 113 largely enclosed working volume by cylindrical displacers 114 in
  • the working fluid can flow around these displacers 114, the gap between the displacer and the cylinder wall acting as a regenerator pointing in the direction of the
  • a single displacer 114 acts like one of the corresponding regenerators 36
  • valves 1 1 1 and 1 12 correspond to the valves 49 and 48, respectively.
  • the displacers 114 are driven, as with the regenerators in FIG. 8, by a bundle of concentric tubes 109, the tube with the largest diameter against the piston 113 and each another tube is slidably sealed to the two tubes with the next smaller or next larger diameter.
  • the drive can then take place with only a relatively small change in the working volume (up to 10%) by means of the piston 113 by means of a lever construction 117 as in FIG.
  • the corresponding connecting rods of the chain drive described in FIG. 8 can act directly on the corresponding tubes of the tube bundle 109.
  • regenerator to be flown through must be arranged inside the displacer and the flow resistance in the gap between the cylinder wall and displacer must be of the same order of magnitude as for the regenerator at a comparable flow rate. This may require an additional seal.
  • the heat transfer surface for cooling through the cylinder wall 1 15 is increased by slots in the stroke direction, the working fluid flows around the displacer in this area and must also flow through a regenerator in this displacer.
  • This machine can also be designed for operation with a liquid as working fluid in the working volume.
  • the technological problems that occurred were solved by Malone in 1931 for water as the working fluid in machines that are similar in construction to a Stirling engine.
  • Sources Malone: A new prime mover- J. of the Royal Society of Arts, Vol 97 1931, No. 4099, p.680-708 or: The development of the hot air engine by Tvo Kolin Professor of Thermodynamics translated into German by Dr. C. Forster page 54, 55 c E.
  • FIG. 22 looks very different.
  • the working volume is largely delimited by a pressure housing 128, inlet and outlet valves 130 and 129a, b.Tn this working volume is caused by the regenerators 131-136 which are stationary relative to the pressure housing and which are connected to the regenerators 131 -135 connected partition walls 137-141, walls of the pressure housing and displacer sealed on these walls, displacer 142-146 partial volumes delimited
  • the periodic size change of these partial volumes corresponds to the periodically changed stroke difference of the corresponding regenerators in FIG. 9T.
  • the Displacers 142-145 are moved periodically simultaneously
  • the racks 146-149 attached to these displacers are driven by gearwheels on a shaft 150a
  • This shaft is sealed out of the working volume by the pressure housing and on it the ends of a chain 150 are wound up or unwound, which is stretched over two chain wheels 151 and on which the connecting rod 152 of such a chain transmission construction acts, which in FIG. 8 attacks the regenerator 36 Drives
  • this chain transmission through the shaft 154 driven by an electric motor, another similar chain transmission 155, which moves the displacer 146 in the same way, is connected in such a way that there is a phase shift of approximately a quarter period with the movement of the other displacers
  • each of the displacers 142-145 in FIG. 22 adjoin one of the partial volumes between two of the regenerators 131-135 and the partial volume adjacent to the cooler 156
  • the displacer 142-145 can practically no longer be flowed around, otherwise the desired balance will not be formed
  • valve 129a can be used like valve 35 in FIG. 1
  • FIG. 22 the construction of FIG. 22 can also be designed or used as an engine, chiller, heat pump Liquid displacement piston
  • the displacement pistons are designed as a vibrating liquid column with a float in a U-shaped container
  • the movement of the liquid displacer piston is controlled and driven by a belt 159 which is tensioned on a shaft 158 and which is attached to the float 157
  • liquid displacer pistons perform largely the same deriodic movements as explained for FIG. 22 with FIG. 9, several of the liquid displacer pistons corresponding to the displacer pistons 142-145 can also be driven from a shaft 158 corresponding to 150a with this construction in the operating state
  • This shaft 158 can be controlled and / or driven as described for FIG. 22
  • valve 160 Before liquid can get past a float 157 into a hot room, which could lead to a dangerous explosion of steam, the valve 160 should be closed by the extreme position of the float 157 and the flow rate
  • this valve 160 remains closed during the time periods abc with the extreme position of the corresponding float by means of a temporary locking.
  • the displacer 157 is also temporarily locked when it hits the seal which is firmly connected to the pressure housing 161 is printed
  • the surfaces of the heat exchanger 162 are heated or cooled by immersion in the oscillating liquid.
  • valve 166 acts as a nozzle. This drives the pendulum movement of the liquid column
  • the working volume for the working fluid which goes through the cyclic process is reduced to increase the compression together with that the total volume of the working volume and the volume of the oscillating liquid by displacing the slidingly sealed piston 167 and increased again in the time period efg
  • the mechanical energy exchanged can at least partially be temporarily stored in the oscillating liquid column, which connects to the piston 167 min two heat exchangers in a pressure housing according to the invention:
  • each of the regenerators 131-134 in FIG. 22 must be provided with a heat exchanger on the same side with regard to the flow as in regenerator 135.
  • the liquid can then flow through these heat exchangers one after the other and thereby exchange thermal energy at several temperature levels (see FIG. 3).
  • the amount of working fluid in the non-overlapping partial volumes of the working volume divided by the regenerators with heat exchangers then largely have the temperature of the heat exchanger . If the working fluid flows into a working volume of an engine according to FIG. 8 in the operating state, it mixes with cooler working fluid. The heat energy given off compensates for the irreversibility through heat conduction, shuttle losses or limited quality of the regenerators.
  • a design based on FIG. 23 or FIG. 21 is also associated with less design effort. since here too the heat exchangers do not have to be moved and the connections for the liquid exchange of the heat exchanger are not a problem.
  • the inlet and outlet valves are arranged as shown in FIG. 22.
  • the gas escapes from the partial volume of the working volume at the highest temperature and the partial volume adjoins the heat exchanger at the corresponding temperature. If the temperature change of the gas during the adiabatic expansion in the external turbine is significantly smaller than the temperature change of the liquid, the gas is released into and out of a (the hottest) partial volume of the working volume by valves.
  • the thermal energy given off by the exhaust gas of a gasoline or diesel engine during cooling can be used to generate additional mechanical or electrical energy or to charge the engine with filtered fresh air at higher pressure and therefore not have to use any mechanical energy for a turbocharger or compressor. whereby, compared to an engine without this supercharging, a better output volume and in any case a better efficiency can be achieved.
  • the thermal energy emitted by the exhaust gas of a gas turbine during cooling can be used to supply the cool gas with filtered, cool fresh air at higher pressure.
  • the compressor of the gas turbine used here can be designed so that it with unchanged pressure in the combustion chamber and with unchanged
  • Gas flow rate requires less drive energy, which leads directly to a greater useful output with the same fuel consumption and better efficiency.
  • the efficiency in this case is greater due to a synergy effect than the sum of the efficiency of the original gas turbine and the efficiency of the thermal compressor (gas compressor), since the power applied by the thermal compressor for gas partial compression from the original compressor of the gas turbine only with less favorable Efficiency can be achieved, driven by the branching of mechanical shaft power. Possibly. it is also possible to use a conventional gas turbine. A relative pressure increase in the gas turbine can then be expected, which decreases continuously from the fresh air inlet to the exhaust gas outlet, as a result of which the power density and efficiency are increased.
  • Glass rods 251 are arranged largely parallel to a plane, which divides the reflected solar radiation from a parabolic trough mirror into two equally strong beams, and almost abutting a plane perpendicular to it through the focal line 250 of the parabolic trough mirror, so that. only a small proportion of the radiation power reflected in the direction of the focal line arrives at the focal line of these elements when the parabolic trough mirror is ideally aligned in the region of the end face
  • the incident sunlight is ultimately reflected in a directed manner and the heat radiation of a black body with a temperature of 700 ° K is absorbed as far as possible.
  • These glass rods are arranged in several rows with only small slits and, together with mirror-pure sheet metal, which has surfaces parallel to them, enclose a flow channel 252 parallel to the focal line 250, which flows from a flow channel 253 parallel to the focal line 250 with a larger cross section through at least one connecting channel 254 Air is supplied and from which the air flows through the slots between the glass rods 251.
  • this air is directed away from the focal line onto an absorber structure 255, where the air is heated by the solar energy as it flows through. Adjacent to the absorber structure is the hottest flow channel 256, which leads the hot air to a collecting channel.
  • the absorption of the solar radiation takes place on surfaces that also reflect directionally, absorb the radiation of a black body at a temperature of 700 ° K and are arranged so that the absorbed energy per surface is as constant as possible, so that the heat transfer from this surface to the Work equipment (despite its low thermal conductivity or heat capacity) with minimal exergy losses.
  • a black body at a temperature of 700 ° K
  • the area of the absorber can be increased by increasing the number of areas which are always aligned in parallel with an increasing number, the air having to flow through only one area from the focal line in order to reach the hottest flow channel 253.
  • At least one glazed flat slotted plate 257 is attached in front of the focal line in the direction of irradiation, in the plane of which the focal line also lies.
  • Beam direction which ensures that a certain amount of air arrives hotter at the absorber structure than without this temperature profile through the formation of a non-linear temperature profile.
  • an entropy transformer is necessary, in which the collector described with Parabolic trough mirror air is heated, which heats a likewise described heat storage and is coupled to this circuit parallel to the heat storage, at least two working volumes connected in parallel, each of which supplies a turbine that drives a generator with compressed air
  • the cooling by water takes place via a large water tank, which serves as an intermediate store, in order to be able to cool the water to lower temperatures at night
  • the secondary claim 155 and the following claims protect a solar collector that heats a gas over a larger temperature interval
  • FIG. 26 An exemplary embodiment characterized in FIG. 26 has two layers of translucent insulation 265, 266 between a transparent cover 260 and an insulated rear wall 261 arranged in parallel between three spaces running parallel thereto with flow channels 262, 263, 264 for the gas.
  • the flow channels run at an angle of 45 ° to the parallel collecting channels 267,268,269
  • Gas is blown from each corresponding flow channel 263 by a fan 272 from the corresponding collecting channel 268
  • These fans 272 are all arranged on a shaft 273 and are dimensioned such that a gas flow flows into each flow channel 263, each of which is largely proportional to the radiation power radiated onto the surface of the corresponding flow channel
  • the translucent insulations 265, 266 consist of either uncoated or coated, the infrared radiation of a black body with a temperature of 700 ° K as much as possible absorbing and the sunlight as possible reflecting reflective metal foil or thin sheet with a corresponding surface and slots 274 parallel to the transparent cover
  • a structure can be achieved by an alternating arrangement of flat and corrugated layers (see corrugated cardboard), whereby a line can be laid through every point of the metal, which runs as far as possible anywhere in the material or at least is not far away from it and is parallel to a main direction which, at least with a suitable orientation, allows direct solar radiation to pass through without significant losses due to absorption or scattering
  • the smallest surface largely surrounded by metal perpendicular to the main direction in the translucent insulation has a size in the range from 0.25 cm 2 to 2 cm 2 T area of the insulated rear wall adjacent to the translucent insulation is optionally an optically selectively coated or blackened metal fabric 275, whereby an increase in flow resistance is achieved.
  • the aim of this flow regulation is to achieve as constant a current flow as possible by means of a maximum area in the translucent insulation the transparency of the gas is used when the translucent insulation is flowed through.Through the interaction of flow, heat conduction and absorption of the radiation energy, a non-linear temperature profile forms, which is flatter on the side of the flowed through insulation in the area of a plane from which the flow in isolation occurs
  • Irradiation direction corresponds to the main direction of the collector. especially when several are connected in series, a very high end temperature can be reached for flat plate collectors
  • a cylinder for example, can be used to immerse a liquid in a container with a vertical axis and a downward opening
  • the valve control is regulated like a historical steam engine.
  • the difference in hydrostatic pressure corresponds approximately to the change in pressure of the
  • a subsystem works like a historic waterwheel without valves
  • Liquid surface of a total container moves
  • the container Due to the rotation, the container is moved in such a way that it predominates
  • the liquid surface of the entire container accelerates.
  • the cover is attached from the side through the side cover, which is attached to the side perpendicular to the shaft axis and is sealed with a sliding seal, as far up as possible
  • Containers supplied or removed in the lowest possible position The other periodic exchange of gas takes place when the container is flooded over the surface of the liquid when it emerges or when it runs empty.
  • This arrangement can also be used for gas compression if the axis is driven in the opposite direction to when it is used as a drive
  • the area of the regenerators 274 - 277 through which flow is required must be increased accordingly.
  • the stationary regenerators 274 - 277 are folded several times along parallel lines 278 at a largely constant distance and enclose at least one disk-shaped displacer element 279, which is periodically moved parallel to it, up to the region of the central axis of the displacement element parallel to the folding edges on both sides. The other half of the displacement element is surrounded by the adjacent regenerator.
  • At least one of the regenerators is optionally connected to a hydraulic or pneumatic piston or diaphragm bellows which can be moved in the direction of movement and which is moved by liquid or gas from the space around the liquid surface of the coupled vibrating surface, which is distant from the corresponding work space Liquid column is filled or filled via control valves.
  • the movement is either by a rod or a tensioned tension element (such as rope or chain) via a movable connection from an endless tension element, like a closed chain or toothed belt, tapped, which is tensioned over several wheels rotating at a uniform angular speed.
  • a tensioned tension element such as rope or chain
  • an endless tension element like a closed chain or toothed belt, tapped, which is tensioned over several wheels rotating at a uniform angular speed.
  • a pipeline system with negative pressure such as the boiler via a heater, is coupled to the inlet valve of a heat engine according to the invention.
  • This system is used as a vacuum cleaner.
  • the effort for the housing 280 around the work space can be significantly reduced if curved shapes are used.
  • the moving regenerators 281 - 284, constructed in the form of a cone shell, have good dimensional stability, can be produced with reasonable effort and can only be driven in the area of the cone tips.
  • each regenerator is connected to a sheet metal cylinder jacket 285 or a comparable jacket of a pointed truncated cone, which is continuously immersed in a liquid 286 at the lower end and thus a flow around the Regenerator prevented during lifting movements parallel to the cylinder axis of the sheet metal jacket
  • Truncated cones which become narrower at the top, are inexpensive and unproblematic as a shape for the sealing element 285 immersed in the liquid and the side housing 280, since the upper region is expanded due to the temperature increase.
  • Concentric tubes 286 are used to drive and guide the regenerators and sealing cylinders, which are guided on an unmoved tube 287 on the common axis of the cylinders and are connected to the regenerators 281-285 in the region of the cone tips ⁇ . In this area, the tubes 286 are provided with at least one slot in the axial direction, through which the internal tubes are connected to the corresponding regenerators 281-284
  • the tubes 287 protrude decisively upwards over the uppermost regenerator 281 into a special bulge 288 of the work space enclosed by the housing and are slidably guided there on an unmoved tube 287.
  • the cylinders 285 are also each connected to one of the tubes 286, which are also slidably guided in this area.
  • the space between the liquid surface 288 and the lowermost regenerator 284 at its lowermost position in the operating state is largely filled by an at least two-part displacer structure 289, which is moved apart during an upward movement and opens flow channels for the working gas on the separating surfaces which run obliquely to be protected.
  • This displacer structure 289 is also guided in the region of the cylinder axis and is either moved via a separate drive or by springs between the regenerator 284 and individual displacer elements and a spring-loaded stop for the stop at the liquid boundary surface 288.
  • this thickener 289 is permanently connected in one piece to the lowermost regenerator 284. so two parts have to be moved less.
  • the dead space becomes larger because of the necessary permanent air channels through the displacer 289 or on its surface.
  • the heat exchanger 290 is either attached directly below the lowest regenerator 284 and flows through a heat exchange medium, or it is attached to the cylinder 285 and / or the corresponding pipe 286 with the lowest regenerator 284 and immersed in the lowest position in the liquid 286.
  • the heat energy is exchanged, which is compensated in continuous operation by a stationary heat exchanger, e.g. is connected to the hot water supply of the building «i
  • Working gas is periodically exchanged through at least one valve 291 in the housing above the uppermost regenerator 281. This exchange is offset by the exchange of working gas. which takes place from the partial space above the lowermost regenerator 284 through at least one piercing pipe attached directly to one end, which is always immersed in the liquid 286.
  • At least one further pipe is then arranged, the upper edge of which extends even further beyond the liquid level.
  • the space is connected by a separate valve, which is controlled together with the gas valve, to a space which is also connected to the space with which the working space exchanges gas through the adjacent pipe.
  • a separate valve which is controlled together with the gas valve, to a space which is also connected to the space with which the working space exchanges gas through the adjacent pipe.
  • it may alternatively be simpler to compare the water level via an additional corresponding pipe arrangement. 295 to check, in which the pipe for the gas exchange is omitted.
  • This pipe cf. 295 is also supplied with water via a further pipe cf. 296, which is used as an overflow and which is arranged in the stroke largely within the liquid with an opening at the level of the largely immobile liquid level without penetrating a regenerator.
  • regenerators 281-284 or elements rigidly connected thereto are rigidly connected thereto
  • the top regenerator 281 directly or indirectly movably engages the main lever at a location that is closest to the location where the direct or indirect mobile connection to the housing is made.
  • One of the lowest regenerators is movably connected via connecting rods 298 to two driven crankshafts 299, which are arranged and moved mirror-symmetrically to a plane in which the unmoving guide element 287 lies in the direction of stroke.
  • regenerators are connected at least to one of the connecting rods, which are supported with the other ends on axles of at least one crankshaft, which can all be cut by a line through the parallel axis of rotation of the crankshaft, whereby the bearing for a connecting rod of the lowest regenerator is furthest from the axis of rotation of the crankshaft and the bearing of the highest regenerator is closest
  • at least one regenerator with a phase shift of a quarter (25 ° o) of a period is given relative to the volume change.
  • the penodic recording takes place when operating as a power machine, and when operating as a heat pump or refrigeration machine, the penodic delivery of working fluid takes place through a valve 291 in the work area adjoins a subspace 301 with a constant volume, which is completely enclosed by two regenerators 302-303. one of these regenerators 302 being relatively directly adjacent to the housing.
  • At least one guide element in stroke 287 is at least partially designed as a threaded rod or ball screw, and an engaging element then moves at least one regenerator connected to it by rotating the threaded rod or Kubelumlspmdel in stroke direction.
  • the threaded rod or ball screw has areas with different pitch heights into which the ⁇ earth elements of the regenerators, which rate differently, intervene so that they are moved at different speeds in rotation when the screw thread or cooling screw rotates, so the number of moving parts can be significantly reduced
  • a heat engine according to the invention can thus be constructed with only five moving parts and the necessary valves.
  • the regenerators are moved up and down penodically when the ball screw rotates at a constant speed in the stroke direction, or at least one threaded rod or ball screw becomes pe ⁇ odically in different directions by using a cube screw and connecting elements with a closed, intersecting thread rotated either by a mechanical control system or directly by a correspondingly controlled motor.
  • the bottom regenerator engages in a ball screw with a closed path and at least some of the other regenerators in rather ordinary thread paths, the paths of which are not closed.
  • the guide tube is flowed through in the middle of working gas from the coolest part of the room either penodically or continuously.
  • a radial ventilator is connected to the pipe with thread or coolant circulation shaft and the pipe in this area is also opened laterally in the coolest part on the other side of the pipe center.
  • a separate pipeline for working gas leads from the space adjacent to one opening of the guide tube to the space adjacent to the other opening in the area of the liquid surface.
  • a valve 312 is attached to the connection from the working space to the tube with the vibrating liquid column, which has a stop in the direction of flow towards the working space, against which the ⁇ valve plate 313 is pressed in a sealed manner as soon as the liquid column has moved too far in the direction of the working space.
  • Another ⁇ L bertikvent ⁇ l 315 coupled to the same space 308 leads instead to the pressure vessel 309 to an external container 316.
  • the Flusstechnikehtand in this container is held constant at the highest possible level.
  • the lowest penodically moving regenerator is a lifting one
  • Pipe 295a fastened, into which gas can flow in and out unhindered from the sub-area adjoining it and whose lower end is always immersed in the liquid.
  • a tube is concentric in this tube 295a, sealingly connected to the housing
  • Liquid of the oscillating liquid column 305 arrives.
  • a pipe 299, the upper edge of which ends in the lowermost subspace at the height of the desired liquid surface 288 in the working space, is connected as far down as possible to the previously described pipe 295, which leads to the oscillating liquid column 305.
  • a valve supplies the working area with a certain amount (e.g. 31) of liquid each time the machine is started.
  • a certain amount e.g. 31
  • the rest of the management of the different amounts of liquid in the machine is done automatically with the construction described above and the functional relationships.
  • the pressure vessel can optionally be replaced by a further working space, in which the thermodynamic cycle takes place with an identical pentode duration offset by half a pentode duration
  • the profile 319 of the channel e.g. worked out with a cursive legend.
  • At least two of these plates are connected substantially in parallel so that both profile edges in the ideal case of j Eder any point be touched by a plate 318 on the perpendicular line.
  • a flexible flat material 320 such as sheet metal or thin (5 mm) plywood is optionally attached to the profile edges 319.
  • the sheet itself can have a reflective surface.
  • Mirrored film or a thin glass mirror must be applied to plywood.
  • mirror trough elements 317 are arranged so that especially in
  • Elements 317 reflected solar radiation can be absorbed on the smallest possible area 321.
  • This structure of the concentrating mirror can be easily integrated on a house roof in terms of construction and architecture:
  • optical concentration factor is also good enough, if only the absorber
  • the edges of the mirror segments 323 emphasize the vertical so that the mirror is more emotionally accepted as a roof.
  • a channel 324 is arranged between two mirror elements, in which water can run off.
  • the mirror system thus forms the top roof skin.
  • the snow-covered structure also has an advantageous effect here, since no horizontally running channels are formed in which water or wet snow can accumulate, causing water to penetrate. Frost damage and leakage can result in the mirror structure being moved around an axis as an alternative. ww yy i m PCT / DE98 / 02827
  • the absorber 322 is sensed and rotated so that its main or symmetry axis 325 corresponds to the main radiation 326 of the absorbed radiation.
  • the absorber 322 is always located in the plane of symmetry of the parabolic nominal mirror 317, as a result of which a good concentration ratio is achieved.
  • the absorber is arranged at a greater distance in the order of the extent of the TWD from the TWD, with the side walls being mirrored, so that a more uniform radiation density occurs at the absorber.
  • the insulated container 328 with a reflecting inner wall forms the rear wall of an upstream solar collector 331. It supplies the heat transfer medium with energy before it can flow through the TWD 327.
  • This collector 331 is supplied with solar radiation energy by a further mirror 332 connected to the absorber 322, which the TWD 327 just missed. Also in this collector 331, the absorber 333 is flowed through by the warm medium ⁇ e__ ⁇ er medium, which the ⁇ g— ' entire absorber structure from
  • Piping system 334 is supplied via at least one movable connection.
  • the absorber structures 322 of a plurality of mirrors aligned in parallel with identical focal lengths are connected relatively directly to a pipeline system 334 which is also moved.
  • a ⁇ bsorber is movably connected via three racks with three fixed points and the distance can be changed with motor power controlled by a shift in the rod direction.
  • At least one absorber 322 is slidably connected to a toothed rack in a controlled manner with motor force, which is movably connected via two further toothed racks with two fixed points each and the distance can be changed in controlled manner with motor force.
  • At least one absorber is movably connected to another absorber and is only moved with two racks.
  • the connecting pipe 334 of the heat transfer medium also fixes the absorber 322 attached to it with respect to the pipe axis.
  • the rotation of an absorber about an axis of rotation perpendicular to the horizontal east-west axis and to the axis of symmetry of the absorber in the main beam direction takes place through the parallel coupling by ropes with a rack, which at 12 noon as close as possible to a vertical plane in the north-south direction
  • the pivot points 336 of the ropes are arranged on one plane through the axis of rotation 337 of the absorber 322 or the axis of rotation of the attachment of the toothed rack to the absorber structure and lie on both sides of these axes of rotation 337, ...
  • an absorber 322 is rotated about an axis of rotation perpendicular to the horizontal east-west axis and to the axis of symmetry of the absorber in the main beam direction by the parallel coupling by rods with a rack, which at 12 noon as close as possible to one vertical plane runs in the north-south direction, the fulcrums of the rods being arranged on a plane through the axis of rotation of the absorber or the axis of rotation of the attachment of the rack to the absorber structure and, when projected into a plane perpendicular to the axis of rotation of the absorber, at least approximately form a parallelogram with a line through the axes of rotation, the ideal angle of which is 90 °
  • the rack is formed by a carrier on which a chain is fastened, in which a sprocket engages, which is driven by a motor via a self-locking gear.
  • the sprocket is guided on the chain by at least one roller that is pressed against the carrier from the other side.
  • a rack can be placed vertically and extended to near the ground so that the A. absorber structure along this rack can be lowered to near the ground by moving the engaging drive.
  • the fulcrum for the absorber structure with gas guide channels 322 is further away from the large main mirror 319 in the beam direction than the fulcrum for the smaller mirror 332 additionally arranged around it
  • the translucent thermal insulation 327 consists of a flat support structure arranged in the radiation direction, e.g. from several slotted sheets with slots arranged perpendicular to the radiation direction, which is surrounded by a transparent and / or especially reflecting structure made of glass fibers in radiation direction, optionally in addition or as a replacement for the glass fibers, glass tubes or rods are arranged in the beam direction.
  • the collector 16 is completely covered by glass 23
  • the TWD 327 is only covered by glass 337 as far as is necessary to guide the heat transport medium air in a flow that is sufficiently parallel to the TWD 327.
  • the currents in the air are controlled in particular when the solar radiation is weakened so that more air is blown out of the collector 331 in front of the TWD 327 than through the TWD 327 is suctioned off.
  • the pollution of the TWD by unfiltered outside air is reduced.
  • the solar radiation energy is concentrated by the mirror structure primarily on the translucent thermal insulation TWD 327 of the absorber.
  • the solar radiation will penetrate at least the front part of the TWD 327 predominantly without absorption and will then be absorbed in the absorber structure.
  • the heat energy can only escape from the absorption area after the decisive obstacles have been overcome by the TWD 327, since the thermal radiation from the absorber or each emitting surface is only largely absorbed by surfaces which have a relatively small temperature difference and which also suppresses convection due to the large areas of the TWD 327 that subdivide the relevant convection space.
  • the flow of the heat transfer medium (eg air flow) is absorbed there in jet direction.
  • the absorber is divided into areas, the flow of which is controlled in a temperature-dependent manner in order to avoid mixing of the heat transfer medium with large temperature differences in the outlet manifold 330.
  • the flowable cross section should remain constant in this area. This is achieved by bimetals 339 regulating the flow, two of which are each connected to a bar 340 like a scale, the suspension of two corresponding bars being movably connected to a centrally suspended bar
  • the pipeline 330 through which the hot gas is removed from the absorber 322 is encased with an insulation 341 with an outer surface 342 with good heat conduction and optionally good or selective absorption, which in turn is largely completely encased by translucent thermal insulation 343 and in one Room 344 ⁇ runs through, which is flowed through by the warm gas of the heat energy cycle on the way to at least one absorber 322 and which for the fall autumn 12:00 noon on the directly illuminated side by an impermeable translucent insulation 345 and on the other side by one
  • Weather protection adjoins and which reflects the incident light, in particular, onto the side of the inner tube 342 which is not directly illuminated, is surrounded and is thus completely encased.
  • a bulk material storage works thermodynamically well and is constructed with a tolerable effort by dividing the bulk material 348 through which the heat transfer medium (e.g. air) flows through at least one insulating, non-flowable intermediate layer 349 into concentric shells with a zvlinderformie jacket with a vertical axis and outwardly curved floor and top surfaces the flowable transitions 350 from an inner shell filled with debris to the adjacent outer shell occur through openings in the insulating cylinder jacket 349, which are arranged on both sides in the area of a plane through the cylinder axis and thus guide the flow through non-flowable connections running in the area of this plane is that the shells can only be flowed through in one direction of rotation about the vertical cylinder axis.
  • the heat transfer medium e.g. air
  • a transition between two half-shells filled with debris is only possible if there is flow through a vertical shaft 351, via which the warrant carrier can also be exchanged.
  • the flow can be controlled in places by reducing the size of the inflow channel in such a way that only heat transfer medium flows in a narrow temperature range in the shaft.
  • One of the outermost insulation layers 352 is flowed through from one fill layer to the other. This results in a decisive curvature of the temperature professional, which means that due to the smaller slope on the cooler side, there is only a lower loss of heat energy flow than without the flow against the temperature gradient.
  • the flow paths are extended by additional, smaller, non-flowable barriers 355.
  • the flow through these bulk material layers 353 is relatively even, the flow paths are approximately the same length as in the cylinder jacket 356 and there is no unfavorable mixing of heat transfer medium at different temperatures.
  • the bulk material storage is heated to well over 100 ° C when the hot and cold air flows in and the bulk material storage is removed a few weeks later by air that flows into the outer storage area at approx. 50 ° C and through one of the Air ducts are removed at 120 ° C - 150 ° C and then cooled by a heat exchanger that heats water from approx. 40 ° C to 100 ° C, which is taken from an insulated water tank in the lower area and fed into the upper area.
  • the waste heat from the ⁇ X arm power engine operated as a hot gas engine is used at Novam to supply energy for heating and hot water.
  • a hot gas engine operated as a hot gas engine
  • a high synergy effect is achieved if the storage tank is not filled with pure water, but with biomull and fakahen.

Abstract

L'invention concerne un procédé et un dispositif pour le transfert d'entropie. Selon l'invention, un cycle périodique se crée à l'intérieur d'un contenant sous pression, par échange périodique de fluide(s) de travail au moyen de soupapes, à des pressions différentes et par modification périodique de volumes partiels qui sont délimités par des régénérateurs, au choix avec ou sans utilisation d'un dispositif de compression. La transformation de l'énergie mécanique par échange de fluide de travail à des pressions différentes simplifie l'intégration d'autres systèmes partiels et la modification de température importante d'au moins un courant de fluide de travail par le couplage d'un cycle thermodynamique de transport d'énergie calorifique, l'accumulation d'énergie calorifique ou la constitution d'un système collecteur solaire de construction simple et efficace, dans lequel la concentration optique, l'isolation translucide et une traversée de cette isolation translucide sont combinées de façon très efficace. L'invention trouve des applications dans l'exploitation de l'énergie solaire ou de sources calorifiques, pour la desserte locale, fonction des besoins, en ce qui concerne la puissance de pompage, l'entraînement mécanique, l'énergie électrique, la mise à disposition de chaleur, la production de froid, le nettoyage ou la séparation, et la modification chimique ou physique d'au moins une substance.
EP98955343A 1997-09-26 1998-09-23 Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique Expired - Lifetime EP1017933B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE19742520 1997-09-26
DE19742660 1997-09-26
DE1997142660 DE19742660A1 (de) 1997-09-26 1997-09-26 Verfahren und Vorrichtung zur Nutzung von Sonnenenergie oder Wärmequellen zur Transformation von Entropie
DE19742520 1997-09-26
PCT/DE1998/002827 WO1999017011A1 (fr) 1997-09-26 1998-09-23 Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique

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EP1017933B1 EP1017933B1 (fr) 2003-08-20

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AT (1) ATE247773T1 (fr)
AU (1) AU753000B2 (fr)
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CN1273623A (zh) 2000-11-15
ATE247773T1 (de) 2003-09-15
NZ503628A (en) 2003-05-30
DE19881421D2 (de) 1999-10-28
AU1223599A (en) 1999-04-23
US6470679B1 (en) 2002-10-29
WO1999017011A1 (fr) 1999-04-08
OA11343A (en) 2003-12-10
EA200000257A1 (ru) 2000-12-25
AU753000B2 (en) 2002-10-03
DE59809356D1 (de) 2003-09-25
EP1017933B1 (fr) 2003-08-20
TR200001624T2 (tr) 2000-10-23
CA2304570A1 (fr) 1999-04-08
JP2001518592A (ja) 2001-10-16
KR20010082498A (ko) 2001-08-30
BR9812554A (pt) 2000-07-25
AP2000001794A0 (en) 2000-06-30
IL135136A0 (en) 2001-05-20

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