WO1992006281A2 - Procede et dispositifs pour transformer librement la chaleur en travail et inversement et pour echanger par approximation les temperatures de deux agents caloporteurs par transfert de chaleur - Google Patents

Procede et dispositifs pour transformer librement la chaleur en travail et inversement et pour echanger par approximation les temperatures de deux agents caloporteurs par transfert de chaleur Download PDF

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Publication number
WO1992006281A2
WO1992006281A2 PCT/EP1991/001804 EP9101804W WO9206281A2 WO 1992006281 A2 WO1992006281 A2 WO 1992006281A2 EP 9101804 W EP9101804 W EP 9101804W WO 9206281 A2 WO9206281 A2 WO 9206281A2
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Prior art keywords
heat
temperature
fluid
work
heat transfer
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PCT/EP1991/001804
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German (de)
English (en)
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WO1992006281A3 (fr
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Adrian Zweidler
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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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/057—Regenerators
    • 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
    • F02G2254/00—Heat inputs
    • F02G2254/30—Heat inputs using solar radiation

Definitions

  • the present invention relates to a method and devices for the free conversion of heat and work into one another. Furthermore, the invention includes a method and devices for the approximate exchange of the temperatures of two heat transfer media, which method and which devices prove to be means for carrying out the methods for the free conversion of heat and work into one another.
  • thermodynamics The second main theorem of thermodynamics is a pure empirical theorem, of which there are different formulations. Today it is considered a natural law. If even one of his formulations proves to be incorrect, this sentence is dropped. The present invention is based on several processes observed in nature, which contradict the statements of the second law and therefore prove that the second law of thermodynamics is not valid.
  • T. is the temperature of the heat transfer medium before converting the heat quantity ⁇ Q into the work W and T_ the temperature of the heat transfer medium afterwards.
  • Gay-Lussac's overflow attempt shows an irreversible process and can only be carried out by using energy or work on the system and corresponding heat dissipation from System can be undone again, the undo result in an indelible change in the environment of the system.
  • Heat can only be converted into work if at the same time part of the heat passes from a warmer to a colder body.
  • entropy There is a state variable, called entropy, whose change is given by the heat supplied to the system in a reversible manner, divided by the absolute temperature. Entropy cannot decrease in a closed system. A machine which would not be subject to the above restriction would be a perpetuum mobile of the second type. Such a machine does not exist (Thomson).
  • thermometer moves a liquid thread or a pointer with every change in temperature. It overcomes friction and thus does work.
  • a permanent change in the thermometer itself cannot be determined over time, so, as the first law of thermodynamics also requires, it must be in constant contact with its surroundings. have a balanced energy balance.
  • a temperature change causes a separate energy circuit for the change in the display.
  • a thermometer is a perpetuum mobile of the second kind! To change the display, it continuously converts the heat into work, which then accumulates as frictional heat.
  • the efficiency of the Carnot cycle only applies to the gas phase to a limited extent and is not generally applicable. For example, if the Stirling process, which is equivalent to the Carnot process in terms of efficiency, is deliberately driven into the liquid with the lower temperature of the working medium. phase, the efficiency ideally assumes the value one.
  • the object of the present invention is to solve this problem.
  • Figure 1 A schematic of the basic principle of the temperature exchange process
  • FIG. 2 A diagram of a method for the approximate exchange of the temperatures of two heat carriers
  • FIG. 3 shows a heat stack store from a grid stack
  • FIG. 4 A wound heat stack store in a perspective view in a partial section during winding
  • FIG. 5 shows a wound heat stack in a front view
  • FIG. 6 shows a temperature diagram of the temperatures T.sub.1 of a fluid and T.sub.g of a heat stack store at a specific point in time when a hot fluid flows through the cold heat stack store;
  • FIG. 7 A temperature diagram of the temperatures Tr of a fluid and T g of a heat stack store at a specific point in time, if the hot one
  • a cold fluid flows through the heat stack
  • FIG. 8 shows a temperature exchanger from a series of spirally rolled tubes in a cross section
  • Figure 9 shows a temperature exchanger from a series of spirally rolled tubes in a side view in a partial section
  • FIG. 10 shows a device for generating a potential for converting heat into work from a vessel with a movable heat stack which communicates with an environment at the upper temperature;
  • Figure 11 A pV diagram with the cycle in the
  • FIG. 12 A device for generating a potential for converting heat into work, the vessel system of which contains a stationary heat stack store and a movable displacer and communicates with the surroundings at the upper temperature;
  • Figure 13 A device for converting heat into a pressure potential of a fluid, the vascular system contains a stationary heat stack and a movable displacer and communicates with the environment at the lower temperature;
  • FIG. 14 A periodically operating device for converting heat into work, which acts as a perpetual mobile of the 2nd type;
  • FIG. 16 A continuously operating system with two devices connected together in a circuit with movable heat stack feeders. rather to convert heat into work, which acts as a perpetuum mobile 2nd type;
  • FIG. 17 two TS diagrams for the opposite representation of the left-hand cycle in the circuit of the plant according to FIG. 16 and the two right-handed cycles in the devices of this plant;
  • FIG. 18 shows a continuously operating system with a device with a stationary and a device with a movable heat stack store, which are connected in a circuit with two loops, for converting heat into work, the system being used as a perpetual mobile 2 .
  • FIG. 19 two TS diagrams for the opposite representation of the state changes in the two loops and the left-handed cycle of the circuit of the system according to FIG. 18;
  • FIG. 20 a continuously operating system with devices for a continuous temperature exchange, which are connected in a circuit for converting heat into work, which system acts as a perpetuum mobile of the 2nd type;
  • FIG. 21 A TS diagram for representing the cycle process in the cycle of the system 20, which describes a figure of eight loop.
  • the temperature of a body If the temperature of a body is changed periodically, it reacts to it with a change in volume corresponding to the course of the temperature. If one opposes this change in volume, the body works on the resistance, which corresponds to the difference between the heat supplied and the heat removed. The body experiences a clockwise circular process. If you add work to the body, the cycle becomes counter-clockwise and more heat must be dissipated than is added to the work.
  • the temperature of a body must therefore be changed periodically between an upper temperature T and a lower temperature T by supplying and removing heat, the body being forced to change the volume by a phase shift compared to its isobaric volume change. As simple as the process is to be understood, as difficult or even impossible it may seem impossible to do it.
  • the method according to the invention for the approximate exchange of the temperatures of two bodies by heat transfer has proven to be the means by which the core problem can be solved.
  • FIGS. 1A) - 1E The basic principle of the method according to the invention for the approximate exchange of the temperatures of two heat carriers by heat transfer is explained below.
  • This basic principle is shown in a very simplified arrangement in FIGS. 1A) - 1E).
  • the initial position of the system under consideration is shown in FIG. 1A), namely the body A at the higher temperature T. and the body B at the lower temperature T 2 .
  • Each of these bodies A, B is now divided into two identical sub-bodies A., A 2 and B., B 2, respectively, which is shown in FIG. 1B). If the body A contains eight heat units arbitrarily adopted than the body B, then its two identical partial bodies A 1 , A 2 each have four heat units more than the partial bodies B 1 , B 2 .
  • heat units which each contain the body or partial body, are indicated as hatched parts of the body for easier understanding. On the left side of the body, the number of the heat units they contain is also given.
  • the heat transfer now takes place in a first step according to FIG. IC), in that the sub-bodies A ⁇ and B. are brought into thermal contact with one another. Temperature compensation takes place here as is conventionally known.
  • the part body A 2 gives two heat units on the part body by B-.
  • thermal contact is made on the one hand between the partial bodies A 1 and B-. and on the other hand made between A ⁇ and B_.
  • the partial body A 1 emits one of its original four heat units to the partial body B and the partial body A ?
  • FIG. 3 shows an advantageous example of such a device, which is called heat stack storage in the following, in a partial exploded view.
  • the heat stack memory consists of a stack of thin-wire copper nets 301, all of which are arranged at a short distance from one another in a heat-insulating manner and are enclosed by a heat-insulating tube 302. This pipe
  • 302 can be made of rings that are put together in a sealing manner
  • 303 consist of a heat-insulating material, for example cork rings 303, between each of which a copper mesh 301 is inserted, as can be seen from the upper part of the figure, which is shown in an exploded view.
  • the fluid flows back and forth through the copper mesh 301 in the stacking direction or pipe direction.
  • FIGS. 4 and 5 show a further example of a heat stack which consists of a winding of a wire with a high heat storage capacity.
  • the winding has a large number of layers and turns and is produced in such a way that the individual layers and turns do not touch anywhere. This is achieved, for example, when a first layer, as shown in FIG. 4, has a profile 401 with x -shaped cross-section and deep thermal conductivity is wound, the individual windings 402 being wound with such a pitch that they do not touch.
  • a strip 404 is then placed on each of the profile long sides 403 for Example glued or clipped on, after which the next layer 405 is wound in the reverse winding direction. The attached strips 404 ensure that the windings of the adjacent layers do not touch.
  • FIG. 5 A finished heat stack store of this type is shown in FIG. 5 in a cross section.
  • the basic profile 501 was expanded with a number of strips 504 and the heat stack store finally has a large number of layers 506.
  • the entire wire coil is enclosed by a heat-insulating square tube 507.
  • Such a heat stack store has a very high heat capacity in comparison to its volume and weight and, despite its industrially suitable production from an endlessly wound wire, is converted into largely discrete heat capacities when a fluid flows through it in the direction of the winding axis becomes.
  • Each individual heat capacity discreetly stores heat at one temperature. It is therefore possible to write temperature information into such a heat stack. If the temperature is varied when inputting, each heat capacity is assigned its own temperature, which can be read backwards out of the heat stack. This is not possible with the conventional heat regenerator.
  • the heat stack store enables the separation of two temperature levels by forming a pushing local boundary between two different temperatures within a medium acting as a second heat carrier. This limit must never migrate out of it, otherwise the desired separation of the temperatures would not be guaranteed.
  • the temperature limit inside such a heat storage stack acts selectively in that external energy can freely pass the limit while internal energy is stopped there.
  • FIGS. 6 and 7 show heat transfers from a fluid to the heat stack store through which it flows and vice versa on the basis of temperature curves T r, T, and both of the flow through
  • FIG. 6 shows these temperature curves, which are location-dependent in the direction of flow, in a snapshot of the situation where hot fluid has already flowed through the initially cold heat stack store for a while and continues to flow through.
  • the arrows indicate both the flow through as well as the shift directions of the curves.
  • the fluid flows from the left at a hot temperature T into the cold heat stack, which was originally located at temperature T 2 with the exception of the heat capacities at the smallest x coordinates.
  • the hot fluid flows into the still cold area of the heat stack, it releases heat from the heat capacities through which it flows until it has cooled to the same temperature as the heat stack, which is at the point where that Fluid has now arrived.
  • the heat stack storage takes on the original temperature - of the fluid.
  • FIG. 7 shows the reverse situation in which cold fluid has already flowed into the hot heat stack from the right for a short while and continues to flow through it.
  • the arrows in turn indicate the direction of flow and the respective direction of displacement of the heat transfer area.
  • the cold fluid at the temperature T 2 thus flows into the hot heat stack, which is at the temperature T., and the heat transition area migrates accordingly, the temperature curves of the fluid and the heat stack again being somewhat shifted.
  • the temperature limit inside a heat stack store is always understood to mean the essential heat transition area with the steep temperature curves as described above. In the real heat stack, this area extends over a certain area in the direction of the fault.
  • FIGS. 8 and 9 show, in a front and partially sectioned side view, such a temperature exchanger which consists of a series of spirally rolled or bent tubes 801 of high thermal conductivity.
  • the individual spirals 901 are aligned with one another with a small spacing.
  • the inner and outer mouths of the spiral tubes 801 are each connected by an axially extending tube 803, 804, 903, 904, whereby the tube spirals 901 are held together. They can also be held together by spacer elements.
  • This temperature exchanger is used for continuous temperature exchange between two fluid heat sources. The first, hot fluid flows through the spirals 801, 901 from the outside in, for example.
  • the second, cold fluid then flows around the individual spirals 901 of the spiral row from a central, for example perforated tube 805; 905 in the radial direction into a jacket perforated tube 806; 06.
  • the individual turns of the spirals form the discrete heat capacities for the fluid flowing past.
  • the steep temperature transition is approximately half the radius of the sprials. It is important that the second fluid can dissipate the same amount of heat as the first one. Otherwise the temperature transition curve would shift slowly and a temperature mixture would take place, which is to be avoided.
  • the described method and the devices for the approximate exchange of the temperatures of two heat transfer media can be used in further methods which ultimately enable the free conversion of heat and work into one another.
  • an energy conversion potential is created while reducing the total entropy, which in the end enables the conversion of heat into work in a second step. While many devices and methods for the second step are known and are used in a large number of different hydraulic and pneumatic work machines and devices, the methods and devices for the first conversion step belong to the essential subject of the present Invention. The generation of an energy conversion potential requires a detailed description.
  • FIG. 10 shows a simplest device for carrying out a method according to the invention for this first conversion step, which uses the method described for the approximate exchange of the temperatures of two heat transfer media.
  • This device does not yet convert heat into usable work, but as preparation for the implementation of such an energy conversion creates an energy conversion potential by generating a local change in the energy density within a system.
  • the device according to FIG. 10 consists of a pressure-resistant vessel 1001 made of little very heat-insulating material inside that contains a fluid.
  • the fluid portion in the upper vessel area 1003 is at the higher temperature T in the gas phase, the fluid portion in the lower vessel area 1004 at the lower temperature T with great advantage, but not necessarily, in the liquid phase. Means not shown are present to keep the two temperatures T, T.
  • a heat stack 1005 is arranged in the interior of the vessel 1001.
  • This heat stack memory 1005 can be moved up and down, for example by means of a mechanical or a non-contact electromagnetic drive.
  • the vessel 1001 is connected on its upper side to an environment which can consist, for example, of a closed circuit.
  • the line 1008 with the one-way valve 1006 leads into a pressure vessel in which the pressure 1 prevails and the return line in which the pressure p 2 ⁇ p- prevails via the line 1009 with the one-way valve 1007.
  • an alternating fluid current is generated at the temperature limit in its interior, which induces an alternating heat flow between the heat stack store 1005 and the fluid.
  • Part of this alternating fluid flow communicates with the environment, while the other part goes through the following cycle and does the compression work on the first part of the alternating fluid flow: a) isochoric heat supply (by moving the heat stack 1005 downward from its uppermost position, that is from the warm side to the cold one, with both one-way valves 1006, 1007 closed), b) isobaric heat supply (by further moving the heat Stack 1005 to its lowest position when fluid is conveyed through the one-way valve 1006 at the pressure p 1 from the vessel 1001 into the environment), c) isochoric heat dissipation (by moving the heat stack 1005 upward from the cold to the warm side, both of which One-way valves 1006, 1007 are closed), d) isobaric heat dissipation by further moving the heat stack 1005 up to its uppermost position when fluid flows through the one-way valve 1007 at the pressure p 2 into the vessel 1001, then again step a), etc.
  • This cycle process is characterized by a rectangle ABCD in the pV diagram, which is run through in a clockwise direction, as shown in the pV diagram according to FIG.
  • This cycle process generates the gas alternating current, which acts in the same direction on the environment by means of the two valves 1007, 1006.
  • the gas flow at pressure p 2 and temperature T flowing into the device via valve 1007 first experiences isobaric heat dissipation as it flows through the heat stack to the lower temperature T, then it is compressed isothermally to the pressure p 1 , whereupon it flows through the heat stack in the opposite direction and thereby absorbs the previously stored heat again isobarously, in order to finally get back into the environment via valve 1006.
  • the compression work is carried out by the previously described cycle.
  • the heat corresponding to this work must be supplied to the fluid in addition to the other heat losses at the upper temperature T, and the same heat must be removed from this fluid at the lower temperature T. It can be seen that the lower the lower temperature T, the lower the compression work and the heat throughput until it finally disappears approximately when the gas or fluid at the lower temperature assumes the liquid, incompressible state of matter.
  • the device works as an isothermal gas pump.
  • FIG. 12 shows an alternative device with a stationary heat stack store, which also acts as an isothermal gas pump. It differs from the device according to FIG. 10 only in the means for generating the alternating fluid flow and, as shown here, includes a vessel system 1201 comprising two cylinders 1206, 1207 that are as heat-insulating as possible, one 1206 of which is the heat stack storage 1205 and the other 1207 contains a piston 1208 acting as a displacer 1208.
  • the displacer 1208 and the temperature limit in the heat stack memory 1205 divide the vessel system 1201 into two variable vessel regions 1202, 1203 with the fluid inside at the two temperatures
  • the fluid portion in the vessel region 1202 is at the higher temperature T in the gas phase, the fluid portion in the vessel region 1203 at the lower temperature T is again advantageously, but not necessarily, in the liquid phase. Means are not shown to maintain the two temperatures T, T.
  • the displacer piston 1208 consists of a gas-tight material with the lowest possible thermal conductivity and small heat capacity. It is mounted inside the cylinder 1207 with as little friction and sealing as possible and can be moved up and down by means of the rod 1209. In this way, a relative movement between the fluid and the heat stack storage 1205 can be generated.
  • the two cylinders 1206, 1207 are connected at the top and bottom via lines 1210, 1211.
  • the upper line 1210 communicates via the line 1212 and the one-way valve 1214 with a pressure vessel in which the pressure p. prevail, and via the line 1213 and the one-way valve 1215 with the return, in which the pressure p 2 ⁇ p .. prevail.
  • the displacer piston 1208 is moved up and down, with which the vessel areas 1202, 1203 move back and forth locally and, as a result, fluid alternating currents and corresponding heat alternating currents with respect to the stationary heat stack memory 1205 be induced.
  • the thermodynamic processes are identical to those which have already been described for FIG. 10.
  • the alternating fluid flow communicates with the environment at the upper temperature T, in that a fluid is taken up from the environment, the fluid isothermally brought to higher pressure and finally released from the pressure vessel to the environment by relaxation . With this relaxation, an actual conversion of the form of energy takes place. Due to the isothermal compression before the expansion, the local energy density of the fluid conveyed from the process space has been increased compared to the fluid absorbed by it at a constant temperature.
  • the energy required to move the heat stack or the displacer is low, since the pressure in the process space spreads equally on all sides. If, for example, the upper part 1216 of the rod 1209 is omitted, a resultant torque can be generated together with the changing pressures within the device on a crank mechanism, so that the device can be executed in a self-running manner.
  • FIG. 13 shows a device in which the fluid, in contrast to the device shown in FIGS. 10 and 12, communicates with the environment at the lower temperature T of the heat stack store 1311. Otherwise, the device also has a vessel system 1301 with the same elements.
  • the vessels are connected to one another via line 1310, and below via line 1302.
  • a further line 1303 leads from the connecting line 1302 via a one-way valve 1304 into a hydraulic accumulator.
  • a line 1306 also leads via a one-way valve 1307 from an open hydraulic container, that is to say connected to the environment, into the line 1302.
  • the fluid contained in the vessel system is kept at two temperatures T, T such that it is in the upper vessel region 1308 at the higher temperature T in the gas phase and in the lower vessel region 1309 at the lower temperature T in the liquid phase.
  • the methods and devices described so far are not entirely self-running. Additional means are required in order to keep the methods and devices in operation. For example, the temperatures in the lower and T upper region of the vessel must be kept and the fluid alternating currents or alternating heat currents must be induced by generating a relative movement between the fluid and the heat stack storage become. The generation of this relative movement as well as the maintenance of the required heat sink on the lower temperature T may be provided with with t ELN that use a small part of the fluidic pressure potential generated accordingly.
  • the fluidic pressure potential can be converted into mechanical work in a known manner by means of an expansion machine. It can be, for example, an expansion turbine for the expansion of a compressed gas or a hydrostat for the conversion of a hydraulic pressure potential.
  • the gas cools down at the same time, which can then be used as a coolant to maintain the required heat sink.
  • a heat pump can be driven, for example, by converting it into mechanical work in order to maintain the two temperatures.
  • FIG. 14 shows a device which includes an additional device for converting the fluidic pressure potential into mechanical energy, a portion of which is then used directly to maintain the operation of the method, while the rest can be used freely.
  • This device is a perpetuum mobile type 2, which has so much heat must eat how it delivers usable mechanical work.
  • the device consists of two cylindrical vessels 1401, 1402, in each of which a piston 1403, 1404 is sealingly mounted.
  • the two pistons 1403, 1404 are phase-shifted with respect to the spatial change they cause, which forces the phase shift of the volume changes of the fluids according to the invention.
  • the coupling advantageously has the effect that the piston 1404 in the second cylinder 1402 leads the piston 1403 in the first cylinder 1401 by a phase shift of approximately 90 °.
  • a heat stack store 1405 Arranged in the interior of the cylindrical vessel 1401 above the top dead center of the piston 1403 is a heat stack store 1405, which represents the main heat stack store 1405 of this device. Above this main heat stack storage 1405 there is a capacitive heat storage 1406, which consists of a material with a high heat storage capacity, for example a thinly rolled copper corrugated sheet, which is like a roll of corrugated cardboard in the vessel along the cylinder axis is ordered and can therefore be flowed through in the direction of the longitudinal axis of the vessel.
  • this heat store 1406 can also be provided, for example, by fine copper wool, which fills this space. It is important that this heat accumulator 1406 can quickly absorb, store and release heat.
  • the cylinder 1401 contains a separating membrane 1408 formed as a bellows 1408 made of sealing, thermally conductive material.
  • This separation membrane 1408 sealingly divides the interior of cylinder 1401 into two variable areas.
  • the space 1409 remaining at this upper cylinder end is dimensioned such that the bellows 1408 arranged therein can be pulled out and collapsed again, the displacement volume of the bellows 1408 between the folded and the unfolded state being at least the stroke volume of the piston 1404 in the second cylinder 1402 corresponds.
  • a pressure line 1410 leads from the upper end of the first cylinder 1401 into the second cylinder 1402.
  • the pressure line 1410 can serve, among other things, to absorb heat and for this purpose can be led through corresponding heating means 1411 or media, so that it flows therein Fluid that can transport heat into the first cylinder 1401. However, the heat can also be absorbed directly in the area above the bellows 1408.
  • the cylindrical vessel 1401 is basically divided into three areas with different temperatures by the two heat stack stores 1405, 1407.
  • the highest temperature T prevails between the two heat stack stores 1405, 1407.
  • the cylinder 1401 basically contains two fluids of different substances below the separating membrane 1408, one of which on the lower te - temperature T of the heat stack storage 1405 is always in the liquid phase and is at its upper temperature T in the gas phase.
  • the second fluid F. is always in the gas phase and occupies the entire free space in the first cylinder 1401 up to the inside of the bellows 1408.
  • the first fluid F water and the second fluid F. nitrogen.
  • the combination of alcohol as F ⁇ would also be suitable. and nitrogen as F SD, liquid carbon dioxide as Fa and nitrogen as F. or liquid nitrogen
  • cylinder 1401 is filled with a temperature-resistant hydraulic fluid F ⁇ rl.
  • F ⁇ rl a temperature-resistant hydraulic fluid
  • Cylinders 1402 are completely filled with this hydraulic fluid F ".
  • This device is a self-running machine which periodically reversibly converts heat into mechanical energy. The use of mechanical energy finally causes the conversion back to heat, which is released to the environment.
  • the device can also draw the heat required for operation from precisely this environment, since when the gas is expanded inside the bellows 1408, heat has to be applied from the outside. Conditional The reason for this is that the temperature T inside the bellows 1408 must be at a lower level than the ambient temperature. In this case, the system is supplied with heat from the environment via the heat exchanger 1411 via the hydraulic fluid F H.
  • the efficiency of such a machine is primarily dependent on the magnitude of the temperature difference between the lower temperature T or T prevailing in the environment and the upper temperature T, which is in the interior of the cylinder 1401 in the heat capacity 1406 prevails, determined. Losses result exclusively from the building materials and components to be used, which are naturally not ideal. Thus, a small proportion of the heat will flow down through the cylinder walls of the cylinder 1401 and also through the heat stack memory 1405, due to its non-ideal characteristics, a small part of the heat will reach the cold side downwards.
  • the lower temperature Tu in the liquid fluid fraction Fa can correspond approximately to the ambient temperature, so that it is maintained by the ambient cooling.
  • the alternating fluid flow of the fluid F liquid at the lower temperature T generated by the piston 1403 at the temperature limit in the main heat stack store 1405 undergoes a cyclic process, which is approximately shown in the TS diagram according to FIG. 15A and successively includes the following steps:
  • FIG. 16 shows a device which combines the various methods and devices according to the invention to form a system which operates continuously and is a second-type perpetuum mobile.
  • This system guides the fluid in an external circuit through two different devices 1601 and 1602 according to the invention, which gradually increase the pressure of the fluid and then through a machine 1616 for converting fluidic to mechanical energy, for example by a known one Expansion machine.
  • the fluid alternating current and thus a heat alternating current is induced in the devices 1601, 1602 shown here by the fact that the heat stack stores 1605, 1607 are moved relative to the fluid even in each device 1601, 1602 according to the invention, for example by means of crank drives.
  • the external cycle process which the fluid undergoes when flowing through the circuit, is counterclockwise and, in addition to converting heat into work, creates the temperature range for maintaining the operation of the two devices for generating the energy conversion potential.
  • the inner circular processes which the fluid alternating currents experience inside the individual devices 1601, 1602 are clockwise, and the areas which they enclose in the pV or TS diagram are a measure of those of them compression work performed per cycle on the outer cycle.
  • the first device 1601 runs between the upper temperature T -. , which advantageously corresponds to the ambient temperature and the lower temperature T .., and the fluid contained therein communicates with the external circuit at the lower temperature T.
  • the first device 1601 absorbs heat from the environment to maintain its upper temperature T -.
  • the upper end of the vessel 1608 has the largest possible surface, so that, for example, a plurality of caps 1621 are formed when viewed from below. Needles 1622 can be inserted into these caps 1621, which sit on the uppermost heat capacity of the heat stack storage 1605, so that only a minimal dead volume remains in the top dead center of the heat stack storage 1605 and a large heat transfer per time from the environment to that intermediate gas is possible.
  • a pressure line 1609 leads through a one-way valve. til 1610 out of the vessel 1608.
  • This pressure line 1609 leads further through heating means 1611 for further heat absorption from the environment and finally via a one-way valve 1612 into the side of the upper temperature T "of the vessel 1615 of the second device 1602.
  • a pressure line 1613 leads from the upper via a one-way valve 1614 Side of the vessel 1615, that is, on the side of its upper temperature T 2 and into an expansion machine 1616. From the expansion machine 1616, a pressure line 1617 leads back to the second device 1602 and there as a cooling coil 1618 around the area of lower temperature T 2 of the vessel 1615 of this device 1602.
  • this cooling coil 1618 leads from the end of this cooling coil 1618 as a pressure line 1619 via a one-way valve 1620 into the lower side of the vessel 1608 of the first device 1601, that is, into the side of its lower temperature T .. If the heat stacks 1605, 1607 in these devices 1601, 1602 and a b move, the fluid enclosed in the described circuit experiences an external, left-handed circular process, while the fluid alternating currents in the devices 1601, 1602 experience right-handed circular processes.
  • the left-handed cycle process is described, which is shown in the left diagram of Figure 17A.
  • point 1 is the fluid as a result of the adiabatic expansion at the lowest pressure p 1 and at the lowest temperature T.
  • the second device 1602 is guided through the cooling coil 1618 at the lower part of this device to maintain the lower temperature T 1 and takes up isobaric heat there, after which it reaches the temperature T 1 .
  • T 1 the temperature of the TS diagram
  • At this temperature it reaches the bottom of the device 1601 and is adiabatically compressed therein, the work of compression being removed from the surroundings in the form of heat at the upper temperature T .
  • This adiabatic compression is described in the TS diagram by the path from point 2 to point 3.
  • the heat sink is held in the device 1601 by the inflow of the fluid at the lower temperature T -.
  • the fluid flows from point 3 through the heating means 1611, which are at the highest temperature T of the entire system. It absorbs isobaric heat there, which corresponds to the path from point 3 to point 4 in the TS diagram.
  • the second device 1602 it is then compressed isothermally, which is described by the horizontal from point 4 to point 5 in the TS diagram. Then it is relaxed adiabatically in the expansion machine 1616 and returns to the state in point 1 as described by the vertical in the TS diagram.
  • the state of the liquid portion of the fluid is represented by point 6.
  • the cycle of the alternating fluid flow in the first device 1601 takes place at lower pressures. It begins at the lower temperature T., still below the lower temperature T.sub .-- of the second device 1602 at point 10. As in the second device, an isochoric heat supply follows from point 10 to point 11 until the one-way valve 1610 opens and fluid can flow out. The further supply of heat then takes place isobarically along the isobars from point
  • the changes in the state of the alternating fluid currents have been considered, the changes in the state of the fluid components which remain at the respective upper or lower temperature can also be considered. Essentially, these fluid components change their pressure approximately along isotherms.
  • the gaseous fluid moves isothermally in the area of the upper temperature T 2 between points 4 and 5 in the diagram on the left and the liquid fluid in the area of the lower temperature T 2 remains at point 6, since a The change in pressure in point 6 cannot be represented.
  • devices 1601 and 1602 are self-running. This is the case because a piston rod protrudes into its interior only on its underside and, at the same time, the internal pressures during the upward movement of the heat stack accumulators are lower than the pressures during the downward movement. This results in torque on the crankshafts.
  • Figure 18 shows another plant for converting heat into work.
  • a first device 1801 is integrated, which communicates with the circuit at the upper temperature T -.
  • the device 1801 has one from the lower side in the cylinder linder 1823 of the device acting piston 1803 and contains a fluid at the lower temperature T ⁇ fluid, for example nitrogen.
  • a pressure line 1804 leads through the one-way valve 1806 into the device and a pressure line 1809 through the one-way valve 1808 out of the device 1801.
  • This device 1801 essentially acts as a pump in that it pumps the fluid through the heat stack store 1805, which absorbs heat there and leaves the device 1801 in the gas phase at high pressure.
  • a bladder accumulator 1810 is connected to the pressure line 1809 in order to compensate for pressure fluctuations in the pressure line 1809.
  • the compressed gas is next expanded in the expansion machine 1811. Part of the work performed by the expansion machine 1811 is used to operate the device 1801.
  • the expanded gas absorbs heat at the lower temperature T 2 of a second device 1802 in order to keep this temperature T 2 there, and then flows through a temperature exchanger 1812, where it again absorbs heat, below more heat absorption by a heat source 1813 and finally via the pressure line 1804 and the one-way valve 1806 back into the first device 1801.
  • the pressure line 1804 is also connected to a bladder accumulator 1814 in order to compensate for pressure fluctuations.
  • the circuit described forms the first loop.
  • a second loop branches off in front of the expansion machine 1811 and leads via the line 1815 and the one-way valve 1816 into the upper area Temperature T_ of the second device 1802.
  • a movable heat stack 1807 is arranged, which can be moved up and down, for example, by means of a crank mechanism.
  • the incoming gas is compressed in the device 1802 and conveyed into the pressure line 1818 via the one-way valve 1817.
  • This pressure line 1818 is also connected to a bubble reservoir 1819 to compensate for pressure fluctuations. It leads the gas as countercurrent fluid through the temperature exchanger 1812, where it gives off heat.
  • the fluid flows with further heat emission through a further temperature exchanger 1820 and then through a throttle 1821. Its now liquefied portion flows back through line 1822 on the side of the lower temperature T m via a further throttle 1824 into the first device 1801 .
  • the still gaseous fraction is used as counter-flowing fluid in the temperature exchanger 1820, where it absorbs heat and then flows back into the pressure line 1808 via the line 1825 in front of the expansion machine.
  • the changes in state of the fluid in the two loops are shown qualitatively in the TS diagrams according to FIGS. 19A and 19B.
  • the states are numbered and correspond to the corresponding numbers in the loops of the circuit.
  • the fluid in the first loop undergoes a left-handed cycle, which is shown in Figure 19A.
  • point 1 when pumping out of the device 1801, it is at the highest temperature T - and the highest pressure.
  • T - and the highest pressure After adiabatic relaxation in the expansion machine 1811, it has reached the state in point 2.
  • the change in state is shown in the diagram on the left as perpendicular from point 1 to point 2.
  • the fluid flowing in the second loop experiences the changes in state shown in the diagram in FIG. 19B.
  • part of the fluid in state 1 is removed at the temperature T Q1 and compressed in the second device 1802 without it absorbing heat.
  • the warmth that is on of the lower temperature T _ between points 2 to 3 is removed by the second device 1802, is not added above and therefore the temperature drops during the compression.
  • the fluid changes its state along a polytropic, which runs between an isobar and an isotherm from point 1 to point 6. It is then passed through the temperature exchanger 1812, where it gives off isobaric heat, corresponding to the change in state from point 6 to point 7 in the diagram.
  • FIG. 20 shows a continuously running system in which only the continuously running method for exchanging the temperatures of two heat carriers flowing uniformly to one another is used.
  • the system consists of a circuit in which the fluid from the state of maximum pressure passes through an expansion machine 2001 and is expanded therein. It then absorbs heat in a first temperature exchanger 2002, is then passed through a heating source 2003, where it continues to absorb heat, and then passes through a compressor 2004, in which it is adiabatically compressed. Then it flows through a second temperature exchanger 2005, in which it gives off isobaric heat and is liquefied. It then continues to flow as a counter-flowing fluid through the first temperature exchanger 2002 already described, in which it continues to give off heat and its temperature drops further in the liquid phase. The liquid fluid is then compressed and conveyed by means of the pump 2006 and flows as counter-flowing fluid through the temperature exchanger 2005, which has also already been described, in which it absorbs isobaric heat, evaporates and regains its original state gc.
  • Adiabatic compression including part of the work gained in the adiabatic relaxation of 1 to 2. This compression is necessary so that the temperature in state 5 is above that in state 1 and that in state 2 is below that in state 7;
  • the expansion machine 2001 delivers the gross power P ß .
  • a portion P p of this output is required as pump output and a further portion P "for driving the compressor.
  • the remaining power P can be used freely.
  • Density of the liquid fluid is required, during which the pure conveying work cannot be represented.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat Treatments In General, Especially Conveying And Cooling (AREA)
  • Control Of Heat Treatment Processes (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

La chaleur et le travail sont mutuellement transformés librement par un processus dans lequel on fait varier périodiquement la température d'un corps entre une température supérieure To et une température inférieure Tu par apport de chaleur et dissipation de chaleur au moyen du procédé d'échange des températures objet de l'invention, le corps étant soumis à une modification de volume déphasée par rapport à sa modification de volume isobare. Dans le procédé d'échange par approximation des températures de deux agents caloporteurs au moyen d'un transfert de chaleur, on place deux agents caloporteurs en contact thermique mutuel sur une section déterminée en les déplaçant l'un par rapport à l'autre dans leur mouvement général, la résistance thermique à l'intérieur de ces deux agents caloporteurs dans le sens de leur mouvement général étant maintenue à un niveau maximum, tandis que dans le sens normal à celui de leur mouvement général la résistance thermique est maintenue à un niveau minimum.
PCT/EP1991/001804 1990-10-01 1991-09-21 Procede et dispositifs pour transformer librement la chaleur en travail et inversement et pour echanger par approximation les temperatures de deux agents caloporteurs par transfert de chaleur Ceased WO1992006281A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3152/90-1 1990-10-01
CH315290 1990-10-01

Publications (2)

Publication Number Publication Date
WO1992006281A2 true WO1992006281A2 (fr) 1992-04-16
WO1992006281A3 WO1992006281A3 (fr) 1992-09-03

Family

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PCT/EP1991/001804 Ceased WO1992006281A2 (fr) 1990-10-01 1991-09-21 Procede et dispositifs pour transformer librement la chaleur en travail et inversement et pour echanger par approximation les temperatures de deux agents caloporteurs par transfert de chaleur

Country Status (2)

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AU (1) AU8508691A (fr)
WO (1) WO1992006281A2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999017011A1 (fr) * 1997-09-26 1999-04-08 Thomas Ertle Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique
EP1942255A1 (fr) * 2007-01-08 2008-07-09 Huseyin Bayir Moteur à énergie recyclable
WO2009011002A3 (fr) * 2007-07-13 2010-08-12 Luigi Maria Murone Moteurs à vapeur à efficacité unitaire
WO2009011001A3 (fr) * 2007-07-13 2010-08-12 Luigi Maria Murone Machines à vapeur, moteurs et appareil de distillation

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH265634A (de) * 1948-07-02 1949-12-15 Saurer Ag Adolph Verfahren zur Herstellung von Wärmespeicherkörpern.
US3077226A (en) * 1956-11-15 1963-02-12 Arrow Ind Mfg Company Heat exchange device
JPS5215947A (en) * 1975-07-25 1977-02-05 Nissan Motor Co Ltd External heat thermal engine
GB2107793B (en) * 1981-10-22 1985-09-18 Malcolm Bicknell Mcinnes Heat engines
US4389858A (en) * 1981-12-03 1983-06-28 Jepsen Henry E Heat engine
US4607424A (en) * 1985-03-12 1986-08-26 The United States Of America As Represented By The Secretary Of The Air Force Thermal regenerator

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999017011A1 (fr) * 1997-09-26 1999-04-08 Thomas Ertle Dispositif et procede pour le transfert d'entropie avec cycle thermodynamique
AU753000B2 (en) * 1997-09-26 2002-10-03 Thomas Ertle Method and device for entropy transfer with a thermodynamic cyclic process
US6470679B1 (en) * 1997-09-26 2002-10-29 Thomas Ertle Apparatus and method for transferring entropy with the aid of a thermodynamic cycle
EP1942255A1 (fr) * 2007-01-08 2008-07-09 Huseyin Bayir Moteur à énergie recyclable
WO2009011002A3 (fr) * 2007-07-13 2010-08-12 Luigi Maria Murone Moteurs à vapeur à efficacité unitaire
WO2009011001A3 (fr) * 2007-07-13 2010-08-12 Luigi Maria Murone Machines à vapeur, moteurs et appareil de distillation

Also Published As

Publication number Publication date
AU8508691A (en) 1992-04-28
WO1992006281A3 (fr) 1992-09-03

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