• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a thermodynamic machine operating between two heat reservoirs after the 2nd Ericsson cycle of 1853. The machine theoretically achieves the efficiency of the Carnot process and can be operated both as a heat-power (legal process) and as a power-heat machine (left-hand process). A combined heat and power engine operating between three heat reservoirs following the Ericsson cycle is also described. According to the invention, compressors and expanders of the gaseous fluid use rotary displacement machines according to the two-shaft rotary piston principle. The rotors (rotary pistons) of compressor and expander are directly in contact with the respective heat reservoir and are designed for heat transfer between fluid and heat reservoir as heat pipes according to the 2-phase thermosiphon principle. This allows a nearly isothermal compression or expansion of the fluid with a low temperature gradient between the respective heat reservoir and the fluid and thus the high efficiency of the thermodynamic machine.
    公开号:AT510602A4
    申请号:T1362011
    申请日:2011-02-02
    公开日:2012-05-15
    发明作者:Otto Hein
    申请人:Otto Hein；
    IPC主号:
    专利说明:

    TECHNICAL FIELD OF THE INVENTION, PRIOR ART
    The invention relates to a thermodynamic machine which operates between two heat reservoirs according to the Ericsson cycle. The machine theoretically achieves the efficiency of the Camot process and can be operated as both a heat and power heat engine. A combination of thermal power and power plant that operates between three heat reservoirs after the Ericsson cycle is also described.
    Thermodynamic machines work in a cyclic process between two heat reservoirs, one at high temperature and one at low temperature.
    A thermodynamic machine that converts heat into mechanical energy is called a heat engine. A thermodynamic machine that generates heat using mechanical energy is referred to as a cogeneration machine.
    An ideal heat engine is supplied with heat from the high temperature reservoir (heat source) and heat is removed from the heat engine to the low temperature reservoir (heat sink). The difference between the amount of heat supplied and the amount discharged corresponds to the mechanical work won.
    An ideal power heater is supplied with heat from the low temperature reservoir and "pumped" into the high temperature reservoir by the mechanical energy supplied. The amount of heat dissipated to the high-temperature reservoir corresponds to the sum of supplied heat and mechanical work
    In the field of thermodynamics, cycles are a sequence of changes in the state of a working medium (liquid, vapor, gas) -all called fluid-which run periodically, whereby the initial state, characterized by the state variables such as pressure, temperature and density, is always reached.
    Circular processes are represented in diagrams (usually pressure - volume, temperature - enthalpy) which describe the sequence of changes in the state of the fluid.
    If the state changes in the diagram go through clockwise, it is a circular process of a heat engine (legal process). By contrast, when running counterclockwise around a power heating machine (left-hand process, e.g., heat pump, chiller).
    Page 1 of 16
    According to the second law of thermodynamics, only part of the heat can be converted into mechanical work. The maximum ratio of delivered mechanical work to supplied heat is called thermodynamic efficiency.
    The thermodynamic efficiency of a heat engine can be calculated from the temperatures of the heat reservoirs.
    η = (Th - Tg / ηη η thermodynamic efficiency Tl temperature of the heat sink, K TH temperature of the heat source, K
    The thermodynamic efficiency of a power heat engine e.g. Heat pump is the maximum ratio of heat given off to supplied mechanical work. It is called COP (CoefFicient Of Performance), and can be calculated from the temperatures of the heat reservoirs. COP = TH / (TH - TL) = 1 / η
    Three cycle processes, which can be traversed in both directions and also achieve the thermodynamic efficiency, are known. These are the Camot, Stirling and Ericsson cycles.
    The state changes of the three processes are shown in the following table.
    Change in status Process A-B B-C C-D D-A Camot isothermal isotrope isothermal isotrope Stirling isothermal isochor isotherm isochor Ericsson isothermal isobar isothermal isobar
    Common to all three cycles are the isothermal state changes. For a heat engine, the isothermal state changes A - B are a compression of the fluid with a discharge of the heat of compression from the fluid into the low temperature reservoir to maintain the temperature of the fluid constant during compression. For a heat engine, the isothermal state changes C - D are an expansion of the fluid with heat from the high temperature reservoir to keep the temperature of the fluid constant during expansion
    Page 2 of 16
    This shows the limits of the processes, a heat flow from the reservoir to the fluid or vice versa requires both a temperature gradient in the flow direction of the heat flow and time. Both reduce the thermodynamic efficiency of practical machines.
    The Camot cycle is a purely theoretical process, so far no machine has become known that even approximates the process. The Camot process is often used as a comparison process for other cycles, the thermodynamic efficiency is often referred to as the Camot efficiency or Camot factor.
    The Stirling cycle is preferably realized with reciprocating engines in various embodiments. In order to achieve the thermodynamic efficiency (Camot Factor), a heat storage / replenisher (regenerator) is required which caches the heat of the fluid after isothermal expansion for later reintroduction to the cold fluid after isothermal compression.
    The Ericsson cycle requires an ideal counterflow heat exchanger (Recuperator) to achieve the thermodynamic efficiency (Camot Factor). With this heat exchanger, in a heat engine, the heat of the fluid after isothermal expansion is returned to the cold fluid after isothermal compression.
    The Ericsson cycle has so far found little practical application. The reason for this is the low efficiency of the heat transfer between the heat reservoirs and the fluid and / or the high structural complexity in order to approximately realize the isothermal compression or expansion.
    From the online encyclopedia under "http://de.wikipedia.org/wiki/Ericsson-Kreisprozess" is known for large heat engines, the multi-stage design of turbo-compressor / expander to approximate the isothermal compression or expansion of the fluid. In each stage, the fluid is isentropically compressed or expanded and then cooled or heated between the individual stages in heat exchangers. The higher the number of stages, the better the change in state of an isotherm approaches, but the higher is the structural complexity.
    The patent EP 0573516 / US 5 394 709, Lorentzen uses instead of the turbo-compressor or expander multi-stage gear compressor or expander and heat exchangers between the individual stages to approximate the isothermal state changes. Again, the construction cost of heat exchangers and piping is very high.
    Page 3 of 16 • ·
    U.S. Pat. No. 7,401,475 B2, Hugenroth et al. describes a thermodynamic system with a nearly isothermal compression or expansion of the gaseous fluid. In this system, a liquid is injected into the fluid stream prior to the compression of the gaseous fluid. During compaction, the liquid droplets absorb the heat of compression, so that the fluid temperature remains approximately the same. After compaction, the heated liquid droplets are separated and the liquid is recooled before being re-injected into the fluid stream. This is analogous to the expander. There, however, a heated liquid is injected into the gaseous fluid stream prior to expansion. The liquid droplets then release their heat as the fluid expands so that the temperature of the fluid remains approximately the same. After the fluid has expanded, the droplets are separated and the liquid is reheated before being sprayed back into the expander inlet. Both fluid circuits represent a high construction cost, but they still have to accomplish the heat transfer from or to the heat reservoirs.
    The patent WO 910 5974 (Al) / US 4 984 432, Corey describes a machine according to the Ericsson cycle using liquid ring compressors.
    In liquid ring machines, a ring of liquid seals the rotor towards the housing.
    The gaseous fluid in the cells of the rotor is in contact with the liquid and can thus exchange heat. The liquid circuits for the compressor or for the expander therefore need heat exchangers, which work together with the two heat reservoirs.
    The published patent application DE 10 2006 038 419A, Friedrichsen describes a rotor cooling for dry-running two-shaft vacuum pumps or compressors. According to claim 1, the shafts of the rotors have an axially extending cavity, in which heat pipes are arranged, which serve to dissipate the heat of compression from the working space to lying outside the working space heat sink. It will be understood from the following description that the temperature gradient between the medium to be compressed and the heat sink is too large to use the compressor for a thermodynamic machine.
    The patent US 6,394,777 B2, Haavik describes a screw pump (compressor) with means for cooling the compressed gas. The shafts of the screw spindles protrude from the compressor housing into a space with cooling liquid, which in turn is enclosed by a water jacket. Parts of the screw spindles and the protruding from the compressor housing shafts are designed as a so-called heat pipes. With this version, the
    Page 4 of 16
    Heat of compaction from the shafts of the screw spindles to the coolant transfer, which in turn gives off the heat to the water jacket. Again, it will be understood from the following description that this compressor is not suitable for a thermodynamic machine. 5
    TECHNICAL OBJECT AND FEATURES OF THE INVENTION
    The invention is based on the object of designing a thermodynamic machine which operates according to the Ericsson cyclic process such that, with little structural complexity, a heat transfer between the fluid and the respective heat reservoir takes place at the lowest possible temperature gradient in order to maximize the thermodynamic efficiency to get close.
    The features of the invention provided for solving this problem emerge from claim 1. The compressors and expander are constructed as positive displacement machines according to a known two-shaft rotary piston principle. According to the invention, in the displacement machines, the rotors protrude out of the housing relative to the input and output side. The surfaces of these projecting rotor sections are for the purpose of heat exchange with the medium of the respective heat reservoir in contact. The medium of the heat reservoir can be liquid or gaseous, and the heat exchange 20 can also take place by means of heat radiation. For the process-conforming heat transport from the fluid to the heat reservoir or from the heat reservoir to the fluid, the rotors are designed as heat pipes according to the 2-phase thermosyphon principle.
    Displacement machines according to the two-shaft rotary piston principle are known in various embodiments. It is common for all types of construction that the two rotary pistons (rotors) rotate in opposite directions in an 8-shaped bore in the housing. The rotors are provided with teeth or cams which mesh closely, separating the inlet and outlet ports of the housing. The teeth or cams may be parallel to or helically disposed about the rotor axis, and their shape and number may be the same or different. As the rotors rotate, the gullets, defined by the housing bore and bore adjustment walls, promote fluid from the inlet to the outlet. In straight-toothed or slightly helical rotors the Hauptforderrichtung of the fluid through the housing is normal to the axes of rotation, with helical teeth or cams, the Hauptforderrichtung is parallel to the
    Page 5 of 16 * · ·
    Rotary axes of the rotors. For many of these positive displacement machines, structural precautions are known for achieving a steady compression of the fluid in the tooth spaces during transport from the inlet to the outlet to allow heat exchange between the fluid and the rotor surface.
    The technology of heat pipes is well known. A heat pipe is a closed at both ends of the tube, which is partially filled with a working fluid, and in which there is a certain pressure inside. The boiling point of the working fluid at a given pressure is the operating range of the heat pipe. Depending on the equipment and pressure used, heat pipes with a working range of a few ° K (helium) up to 2200 ° K (silver) are produced.
    The simplest construction of a heat pipe results in a predominantly vertical application of the same, this design is called 2-phase thermosiphon. If heat is supplied to the lower end of the 2-phase thermosyphon from a corresponding heat source, a part of the working medium evaporates and rises centrally in the interior of the tube. If the upper end of the heat pipe in contact with a corresponding heat sink, then the steam condenses on the inside of the tube and gives off its heat, whereupon the again liquid working fluid flows downwards by gravity along the inner tube wall.
    In heat pipes which are mainly used horizontally, the inner tube wall between evaporation evaporation and condensation zone is provided with a porous material. The return of the working fluid is carried out by the capillary forces in the porous material. This version of a heat pipe is mainly called "heat pipe". Heat pipes that rotate around the horizontal axis are usually executed with a conical or stepped inner bore. The smaller diameter of the bore is in the condensation zone, the larger diameter in the evaporation zone. The speed of a rotating heat pipe of this type must be so high that the centrifugal acceleration on the condensed liquid is greater than the gravitational acceleration. This ensures that the liquid working fluid is evenly distributed in the region of the evaporation zone on the inner tube wall. The centrifugal force also provides for the transport of the liquid from the condensation zone with the smaller bore diameter to the evaporation zone with the larger bore diameter. Heat pipes can transport amounts of heat that are up to a factor of 10,000 higher than a solid copper cylinder of the same cross-section. Along the axis of the
    Seite 6 von 16 • 9 • «» * • * • * heat pipe, the temperature is almost the same. For the use of a heat pipe for heat transport in a thermodynamic machine, the high heat transfer and the small temperature drop along the axis alone are not enough. Important for high efficiency is also that the temperature difference between the heat source and the heat sink is minimized.
    The medium of the heat source is in contact with the surface of the one end of the heat pipe, the heat transfer is carried out first by convection, followed by a heat conduction through the tube wall to the evaporation zone. In reverse order, heat transfer occurs at the other end of the heat pipe, from the condensation zone through the pipe wall to the surface in contact with the heat sink. In order to keep the temperature difference between heat source and heat sink as small as possible for a given heat flow, the surfaces that are in contact with the media from the heat source or heat sink, as large as possible. Furthermore, the pipe walls in the region of the evaporation zone and the condensation zone are to be kept as thin as possible and the pipe material must have a high thermal conductivity.
    Further advantageous embodiments and arrangements of the machine components are set forth in claims 2 to 6.
    LIST OF DRAWING FIGURES
    In the following, the prior art and a particular embodiment of the invention will be explained in more detail with reference to the accompanying drawings.
    Hereby shows: FIG. 1 the p-v diagram of the Ericsson cycle; FIG. 2 the T-s diagram of the Ericsson cycle; 3, the T-s diagram with the amounts of heat that are supplied or removed; FIG. 4 shows the T-s diagram with the amounts of heat exchanged in the heat exchanger, FIG. Figure 5 shows the layout of an Ericsson open-cycle heat engine; FIG. Figure 6 shows the layout of an Ericsson closed loop power heater;
    Page 7 of 16
    * * * «« * * * * * * * # * · · · * * * * V »« i < * * * «* ** · · FIG. 7 shows a cross section through a rotary displacement machine according to the two-shaft rotary piston principle; FIG. 8 is a longitudinal section through a rotary positive displacement compressor according to claim 1; FIG. 9 is a longitudinal section through a rotary displacement expander according to claim 1; FIG. 10 shows the serial arrangement of positive displacement compressors, FIG. 11 shows a heat engine with parallel displacer expander, FIG. 12 shows a heat engine with separate arrangement of compressor and expander, FIG. 13 shows a combination of a heat engine and a power heat engine in use as a heat pump, FIG. 14 shows the p-v diagram for the machine of FIG. 13, FIG. FIG. 15 shows the T-s diagram for the machine of FIG. 13th
    DESCRIPTION OF THE FIGURES
    In FIG. 1, the pressure of the fluid is plotted against the specific volume (p, v diagram). The hyperbola A-B represents the isothermal compression of the fluid, the horizontal B-C the isobaric state change. The hyperload C-D is the isothermal expansion and the horizontal D-A is the isobaric state change of the Ericsson
    Cycle.
    In FIG. 2, the temperature of the fluid is plotted against entropy (T-s diagram). The curves A-B, B-C, C-D and D-A correspond to those of FIG. 1. The clockwise arrow in area A-B-C-D indicates the sequence of state changes for a heat engine. The area A-B-C-D corresponds to the specific mechanical work W that the heat engine delivers.
    The T, s diagram in FIG. FIG. 3 shows the specific heat qA-β dissipated in the isothermal compression A-B and the specific heat qc-D supplied in the isothermal expansion C-D. The dissipated heat qA-β also corresponds to the specific heat supplied
    Page 8 of 16
    external work Wa-b or the supplied heat qc-D also the discharged specific external work WC-d-qA-B = Wa-b = R Tl ln (p, / p0) J / kg qc-D = Wc-d = R Th lti (pi / po) J / kg
    R specific gas constant of the fluid J / kg, K
    Tl, Th temperatures of the fluid K po, pi pressures of the fluid N / m2
    The T, s diagram in FIG. Figure 4 shows the amounts of heat exchanged between the two isobaric state changes of the cyclic process by means of an ideal countercurrent heat exchanger (often referred to as a recuperator). The heat qD-A of the fluid (area under D-A) after the isothermal expansion is returned to the cold fluid after the isothermal compression (area under B-C): qD-A = cp (Th-Tl) J / kg
    Cp specific heat capacity of the fluid J / kg, K Tl, Th temperatures of the fluid K
    The diagrams in FIGS. 1 to 4 are in principle also valid for power heat machines, that is to say for refrigerators or heat pumps. The heat reservoir with the low temperature TL becomes the heat source, the reservoir with the high temperature TH the heat sink. The graphs are reversed counterclockwise with sequence A-D-C-B-A. The area A-D-C-B in the diagram of FIG. 2 corresponds to the specific mechanical work W which is supplied to the power-heating machine. The amounts of heat in the diagram of FIG. 3 change their direction of flow, the heat qA-β is supplied to the cycle and the heat qc-o is dissipated. The supplied heat qA-B also corresponds to the discharged specific external work WA-b and the dissipated heat qc-D and the supplied specific external work Wc-d. The heat flow in the diagram of FIG. 4 also changes its direction. The heat qc-β of the fluid, corresponding to the area under the hyperburden C-B, is recycled in the countercurrent heat exchanger to the cold fluid after expansion B-A. FIG. 5 shows the system diagram of a heat engine according to the Ericsson cycle. This is an open circuit, since the fluid, here air, is drawn in from the environment and, after passing through the cycle, back to the environment
    Page 9 of 16
    is delivered. The compressor 1 compresses the air sucked from the environment A isothermally to the pressure pi, wherein the supplied mechanical compression work Wa-b in the form of heat qo-A to the heat sink with the temperature Tf, is discharged. The air then flows on the way from B to C isobar the countercurrent heat exchanger (Recuperator) 2 and is heated to Th, before flowing at C in the expander 3. In the expander 3, while supplying the heat qc-D from the heat source with the temperature Th, the air is isothermally relaxed to the pressure po. The expander 3 gives off the mechanical work WC-d. The air then flows through the countercurrent heat exchanger on the way from D to A isobar and gives off its heat qD-A to the countercurrent. It cools to the temperature Tl before it is released into the environment A. The difference of the external mechanical work gives the converted specific work W, which drives a generator 4, which in turn supplies the electrical energy in the power grid 5. W = Wc-D-WA-b = R (T "-TL) ln (p, / po) J / kg FIG. 6 shows the system diagram of a power heating machine according to the Ericsson cycle. It is a closed circuit, the gaseous fluid circulates in the system. Before the fluid from A enters the countercurrent heat exchanger 6, it has the pressure po and the temperature TL. In the heat exchanger, the fluid is isobarically heated to the temperature Th before it flows into the compressor 7 at D. The compressor 7 compresses the fluid isothermally to the pressure pi, wherein the supplied mechanical compression work Wd_c is discharged in the form of heat qo-c to the heat sink with the temperature Th. The fluid then passes isobar through the countercurrent heat exchanger on the way from C to B and gives off its heat qc-B to the countercurrent before flowing into the expander 8 at the temperature Tl. By supplying the heat qe-A from the heat source with the temperature Tl, the fluid is isothermally relaxed from the pressure pi to the pressure po. The expander 8 outputs the mechanical work Wb-a. The difference of the external mechanical work of the compressor 7 and expander 8 must be applied by the motor 9, which in turn relates the electrical energy from the power grid 10. W = WD.C-Wb-a * R (Tu-TL) ln (p, / p0) J / kg FIG. 7 shows a simplified cross-section through a rotating displacement machine according to the two-shaft rotary piston principle. In the housing 11 with the inlet opening 12 and the outlet opening 13, the two rotors (rotary pistons) 14 and 15 are rotatably arranged.
    Page 10 of 16 • «· · < * Μ * * * • * * * * * * * * * · · ·
    When using the positive displacement machine as a compressor, the rotors 14 and 15 are mechanically driven in the arrow direction. The tooth gaps of the rotors 14 and 15 require the fluid from the inlet opening 12 with the low pressure to the outlet opening 13 with the higher pressure, the fluid is compressed.
    When using the positive displacement machine as an expander there is a higher pressure at the inlet opening 12 than at the outlet opening 13. The two pressure rotors between the inlet opening 12 and the outlet opening 13 drive the two rotors 14 and 15 in the direction of the arrow and release a torque. The fluid is thereby relaxed.
    When the ambient temperature is different than the fluid temperature in the positive displacement machine, the surface of the housing 11 is either provided with insulation 16 or the surface is directly in contact with the respective heat reservoir to prevent heat flow from the fluid to the environment or vice versa.
    The size of a displacement machine is determined by the displacement. Suction volume is the volume of fluid that is required for one revolution of the rotor without changing the pressure from the inlet 12 to the outlet 13. FIG. 8 shows a vertical section through a rotating two-shaft rotary displacement machine in use as a compressor of a heat engine according to claim 1 of the invention.
    In the housing 11 and the bearings 17,18,19 and 20, the rotors (rotary piston) 14,15 are rotatably mounted. The drive of the rotors 14,15 via the shaft 21, the clutch 22 and the gears 23 and 24, which serve to synchronize the rotors. The two rotors 14,15 protrude opposite the drive side of the housing 11 and are on the ribbed surface 25,26 directly into contact with the medium of the heat reservoir 27, here, for example, the passing air from the environment.
    For process-conforming heat transfer from the fluid to the heat reservoir 27, each rotor 14, 15 is designed as a 2-phase thermosyphon. The cylindrical cavity 28,29 of each rotor 14,15 is partially filled with a liquid working fluid 30,31, also a certain pressure is set in each cavity 28,29.
    Page 11 of 16 * ft * * * * * «· · · * *« «· · · ·« «· · · · ·« · · · · · ftft
    The boiling point of the working fluid 30,31 and the resulting adjusting vapor pressure in the cavity 28, 29 is the operating range of the heat pipe.
    In operation, heat flows from the fluid via the toothed or cammed rotor surface 32, 33 and through the rotor wall to the evaporation zone 34, 35, at which the working fluid 30, 31 evaporates. The steam 36, 37 rises along the axis of rotation of the rotor 14, 15 upwards. If the temperature of the condensation zone 38, 39 is slightly lower than the boiling temperature of the working fluid 30, 31, the steam 36, 37 condenses thereon, thereby releasing the heat of vaporization. The heat flows from the condensation zone 38, 39 through the rotor wall and is discharged via the ribbed surface 25, 26 to the medium of the 10 Wärmereservoire 27th The condensate 40,41 of the working fluid 30,31 flows along the wall of the cavity 28,29 back to the Verdampfimgszone 34,35. FIG. 9 shows a vertical section through a rotary displacement machine according to the two-shaft rotary piston principle in use as an expander of a heat engine 15 according to claim 1 of the invention.
    The expander of Fig. 9 is geometrically similar to the compressor of Fig. 8. Components with the same function have the same name.
    Turning the expander of FIG. 9 and the compressor of FIG. 8 a heat engine with the same speed, so are the absorption volumes of the two machines in the ratio 20 Th / Tl, the temperatures of the respective Wärmereservoire.
    In the housing 11 and the bearings 17,18,19 and 20, the rotors (rotary piston) 14,15 are rotatably mounted. The output of the mechanical work of the rotors 14,15 via the gears 23 and 24, which are used for synchronization of the rotors, and the clutch 22 and the shaft 21. The two rotors 14,15 project opposite the drive side of the housing 11th and are in direct contact with the medium of the heat reservoir 42 via the ribbed surface 25, 26, for example the hot exhaust gases and the radiant heat from the flames.
    For process-conforming heat transfer from the heat reservoir 42 to the fluid, each rotor 14, 15 is designed as a heat pipe according to the 2-phase thermosiphon principle. The cylindrical cavity 28, 29 of each rotor 14, 15 is partially filled with a liquid working medium 30, 31, and a certain pressure is also predetermined in each cavity 28, 29.
    Page 12 of 16
    The boiling point of the working fluid 30,31 and the resulting adjusting vapor pressure in the cavity 28,29 give the operating range of the heat pipe.
    In operation, heat from the fluid flows over the ribbed surface 25, 26 and through the rotor wall to the evaporation zone 34, 35, at which the working fluid 30, 31 evaporates. The Dampf36,37 rises along the axis of rotation of the rotor 14,15 upwards. If the temperature of the condensation zone 38, 39 is slightly lower than the boiling point of the working fluid 30, 31, the steam 36, 37 condenses thereon, thereby releasing the heat of vaporization. The heat flows from the condensation zone 38, 39 through the rotor wall and is delivered to the fluid from the toothed or cammed rotor surface 32, 33. The condensate 40,41 of the working fluid 30,31 flows along the wall of the cavity 28,29 back to the evaporation zone 34,35.
    Since the fluid temperature is higher than the ambient temperature, the surface of the housing 11 is provided with insulation 16 to reduce heat flow from the fluid to the environment. FIG. 10 shows a 3-stage compressor for a thermodynamic machine according to claims 1, 2, 3 and 4 of the invention. The three stages 43,44 and 45 are arranged in series in the fluid flow and serve to increase the pressure from the inlet pressure po to the final pressure p3 = pend. The individual stages are driven by the drive shaft 46 via the transfer case 47.
    Multi-stage compressors are suitably designed so that each stage performs the same compaction work. This is achieved with an equal pressure increase π per stage, π = Pn / Pn-1 = (pend / Po) 1 ^ π pressure increase per stage n number of stage z number of stages Pn-l, Pn pressure before or, after each stage PO, Pend Pressure at the inlet or outlet of the multi-stage compressor The flow Qn from each stage is proportional to the displacement q "and the rotor speed n" and inversely proportional to the pressure increase π. Qn ~% / Λ
    Page 13 of 16 * ·· * * * * * * * • • · · · · · ················. Figure 11 illustrates a heat engine operating between two heat reservoirs at different temperatures according to the Ericsson cycle, converting heat into electrical energy.
    The heat reservoir with the high temperature Th here are the hot exhaust gases and the radiation of the flames 48 of a combustion. The heat reservoir 49 with the low temperature Tl and the fluid of the cycle is here the air from the environment. The ratio of the two temperatures Th / Tl is here assumed to be 3.
    The compressor 50 and the three expander stages 51a, 51b, 51c are designed according to claims 1 to 4. The compressor 50, the three expander stages 51 a, 51 b, 51 c and the generator 52 are connected to each other via the transfer case 53.
    The compressor 50 and the three expander stages 51a, 51b, 51c rotate at the same speed.
    The fluid is sucked from the compressor 50 from the environment 49 and isothermally compressed. The fluid then flows through the countercurrent heat exchanger 54 and is heated therein by the countercurrent of Tl to Th. In the three expander stages 51a, 51b, 51c, which are arranged in parallel in the fluid flow, the fluid is isothermally expanded.
    The fluid then flows through the countercurrent heat exchanger 54 and releases its heat to the countercurrent. The fluid cools from Th to Tl before it exits into the environment 49.
    The compressor 50 of the heat engine is single-stage and the expander is designed in three stages, wherein the three expander stages 5la, 51d, 51c are arranged in parallel in the fluid flow.
    Neglecting the heat losses in the cycle, then the fluid flows and the heat exchanged with the heat reservoirs 48,49 heat quantities of expander 51a, 51b, 51c and compressor 50 behave like the temperatures of the two heat reservoirs 48, 49. At the here assumed temperature ratio Th / Tl = 3, therefore, the single-stage compressor 50 and each of the three stages 51a, 51b, 51c of the expander have the same displacement. FIG. Fig. 12 illustrates a heat engine in which compressors and expanders are spatially separated from one another and without mechanical connection to each other.
    Page 14 of 16 • · • *
    The presented heat engine converts solar radiation into mechanical energy, with which a generator is driven, which in turn supplies electrical energy into a power grid.
    The solar radiation 55 is focused by means of Fresnel lenses 56 and focused on the expander 57 5. The heat input into the expander 57 takes place at a high temperature.
    The fluid of the cycle is here the air from the environment 58. From the compressor 59, the fluid is isothermally compressed and conveyed into the pipe 60. The heat of compression is delivered to the environment 58.
    The expander 57 and the associated countercurrent heat exchangers 61 are arranged in parallel in the flow of fluid. The advantage of this arrangement is that the fluid in the
    Pipeline 60 has ambient temperature, and thus no heat losses occur. Also, the fluid flowing from the countercurrent heat exchanger 61 into the environment 58 again has the ambient temperature.
    The compressor 59 is driven by the electric motor 62, which receives its electrical energy 15 from the power grid 63, not shown.
    The generators 64 convert the mechanical energy from the expanders 57 into electrical energy and supply them to the power grid 63. FIG. 13 shows the combination of a heat and a heat engine The machine operates between three heat reservoirs and is used as a heat pump for space heating. The heat pump receives its drive energy from combustion.
    The heat reservoir 64 with the low temperature Tl is shown as cold water flow, the heat reservoir 65 with the high temperature Th are the hot flue gases and the radiation of a combustion. The heat supplied to the machine from the two heat reservoirs 64, 65 are dissipated by it to the heat reservoir 66 with the mean temperature Tm as room heat.
    The thermodynamic machine consists of the compressor 67 and the two expanders 68,69, which are connected to each other via the gear 70. The two 30 countercurrent heat exchangers 71, 72 are used for process-compatible heat exchange.
    Page 15 of 16
    The fluid of the cyclic process passes through in the direction of the arrow. The letters A to G are used to identify the state changes of the fluid in the following p-v and T-s diagrams.
    A drive for starting the combination of a thermal power with a 5 power heater is not shown in FIG. 14 shows the p-v diagram of the heat pump of FIG. 13. The state changes of the fluid follow the letters A through G and back to A. The intersection E on the isobars D-F separates the cyclic process into a left-hand followed by a recharge process. FIG. Fig. 15 shows the T-s diagram of the heat pump of Fig. 13. The state changes of the fluid follow the letters A to G and back to A. The intersection E on the isobars D-F separates the cyclic process into a left one followed by a right process.
    The heat pump is supplied between C - D heat from the heat reservoir with the temperature TL and between F - G heat from the heat reservoir with the temperature Th. The heat to be dissipated between A - E from the legal process, as well as the heat to be dissipated between E - A from the left process is delivered to the heat reservoir at the temperature Tm.
    The internal heat exchange of the cycle takes place in the left - hand process from B - C to D - E and for the legal process from G - A to E - F.
    The thermodynamic efficiency COP of this heat pump is the maximum ratio of heat given off to the heat supplied and can be calculated from the temperatures of the three heat reservoirs. COP = TM (TH-TL) / T "(TM-TL)
    Page 16 of 16
    权利要求:
    Claims (6)
    [1]
    PATENT CLAIMS 1. Thermodynamic machine operating between at least two heat reservoirs of different temperature according to the 2nd Ericsson cycle, characterized in that the compressor (s) and expander (s) are rotating 5-rotor rotary displacement machines with toothed or cam-mounted rotors (Rotary piston) are constructed so that the rotors protrude from the housing with respect to the input and output side and the surfaces of these protruding rotor sections for the purpose of heat exchange with the respective heat reservoir in contact and that the rotors (rotary piston) for the 10 process-compliant heat transport between the fluid and the respective heat reservoir are designed as heat pipes according to the 2-phase thermosiphon principle.
    [2]
    2. Thermodynamic machine according to claim 1, characterized in that each rotor of a displacement machine has at least six teeth or cams which are arranged parallel to the helical or 15 around the rotor axis, and that the number of teeth and / or tooth shape of the two rotors are equal or unequal,
    [3]
    3. Thermodynamic machine according to claim 1, characterized in that the rotors of metallic or ceramic materials with high thermal conductivity 20 and that possibly parts of the rotor surface and / or the bore of the thermosyphon section are coated with suitable materials such that thus a high temperature resistance , Corrosion resistance, gas tightness and / or wear resistance is achieved.
    [4]
    4. Thermodynamic machine according to claim 1,2 and 3, characterized in that the compressors and / or expander are formed in one or more stages, wherein in the multi-stage design, the individual stages are arranged either serially or in parallel in the fluid stream.
    [5]
    5. Thermodynamic machine according to claim 1, 2, 3 and 4, characterized in that the compressor and expander spatially separated from each other and without mechanical side 1 of 2

    Are connected to each other, and that the compressor is driven by an electric motor, which derives its electrical energy from a power network, and that the expander drives a generator that supplies the electrical energy into the mains, wherein the counter-flow heat exchanger in the vicinity of Expander is arranged. 5
    [6]
    Thermodynamic machine according to claim 1,2, 3 and 4, characterized in that the machine operates between three heat reservoirs and consists of a compressor, two expanders and two countercurrent heat exchangers arranged so that the fluid in a row - And passes through a legal process, wherein the 10 heat exchange of the compressor with the heat reservoir with the middle temperature, an expander with the heat reservoir with the low temperature and the second expander with the heat reservoir with the high temperature in connection. Page 2 of 2
    类似技术:
    公开号 | 公开日 | 专利标题
    DE102005013287B3|2006-10-12|Heat engine
    DE102009057210B4|2015-05-28|Stirling evaporator heat power plant
    WO2016055263A1|2016-04-14|Device and method for the operation of a heat transfer station
    AT510602B1|2012-05-15|THERMODYNAMIC MACHINE WITH ERICSSON CIRCULAR PROCESS
    DE102011118042A1|2013-05-16|Method for producing heat and cold in left-running cycle, with thermal compressor in e.g. refrigerating apparatus, involves vaporizing superheated steam by heat source, and conveying steam to output point of left-running cycle
    DE609405C|1935-02-14|Air cooling machine
    DE102010017943A1|2013-03-21|Heat engine with isochoric isobaric cycle
    DE19814742C1|2000-01-05|Rotary heat engine
    DE102008004075A1|2009-07-30|Stirling engine
    DE102015105878B3|2016-06-23|Supercritical cycle with isothermal expansion and free piston heat engine with hydraulic energy extraction for this cycle
    DE102007047642B4|2010-01-14|refrigeration machine
    DE102007028181A1|2008-12-24|System of rotary piston engines for multilevel utilization of fuel energy in combined process, has rotary piston engines, which work with similar torque-characteristics on common shaft
    DE10035289A1|2001-03-29|Device to generate mechanical energy using heat engine; has Stirling motor with warm and cool sides and refrigerator to cool cold side, with cooler connected to evaporator of Stirling motor
    EP2326821A2|2011-06-01|Heat engine, and method for the operation thereof
    DE10160593B4|2004-07-29|Thermal power plant
    DE102010027347A1|2012-01-19|Device for carrying out a thermodynamic cycle
    DE102019100539A1|2020-07-16|Multi-stage heat pump system with rotary piston machines connected in series
    DE10000082A1|2001-05-17|Steam engine and method for operating steam engines for applying a power-heat link and utilizing reproductive fuels vaporizes amounts of operating substances needed for making steam by pumps and valves controlled in cold area
    DE102008048639B4|2010-10-07|Heat engine and method of operating the same
    EP3486473A1|2019-05-22|Method for using small temperature differences for operating heat engines designed for the conversion of thermal energy into mechanical energy
    DE102008048641B4|2010-10-07|pressure generator
    WO2002084078A1|2002-10-24|Rotary piston thermal engine device
    DE102015013895B4|2020-06-18|Building technology hybrid system
    WO2020002702A1|2020-01-02|Tesla-type turbine, method for operating a tesla-type turbine, apparatus for converting thermal energy into mechanical energy, method for converting thermal energy into mechanical energy and method for converting thermal energy into electrical energy
    AT520661A1|2019-06-15|Thermodynamic machine with Ackeret-Keller cycle process
    同族专利:
    公开号 | 公开日
    AT510602B1|2012-05-15|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    DE102012024031B4|2012-12-08|2016-12-29|Pegasus Energietechnik AG|Apparatus and method for converting thermal energy with an expander|GB1202125A|1967-05-09|1970-08-12|Reinhold Schmidt|A rotary internal combustion engine|
    DE2159274A1|1971-11-30|1973-06-07|Klaus Bruchner|CIRCULAR PISTON HOT GAS ENGINE|
    US4984432A|1989-10-20|1991-01-15|Corey John A|Ericsson cycle machine|
    JP2009270559A|2008-05-07|2009-11-19|Teratekku:Kk|Rotary type external combustion engine|AT520661A1|2017-11-24|2019-06-15|Hein Otto|Thermodynamic machine with Ackeret-Keller cycle process|
    法律状态:
    2016-12-15| MM01| Lapse because of not paying annual fees|Effective date: 20160202 |
    优先权:
    申请号 | 申请日 | 专利标题
    AT1362011A|AT510602B1|2011-02-02|2011-02-02|THERMODYNAMIC MACHINE WITH ERICSSON CIRCULAR PROCESS|AT1362011A| AT510602B1|2011-02-02|2011-02-02|THERMODYNAMIC MACHINE WITH ERICSSON CIRCULAR PROCESS|
    [返回顶部]