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
  • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G1/00—Hot gas positive-displacement engine plants
  • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
  • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
  • F02G1/053—Component parts or details
  • F02G1/055—Heaters or coolers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • 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
  • F02G2243/00—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes
  • F02G2243/30—Stirling type engines having closed regenerative thermodynamic cycles with flow controlled by volume changes having their pistons and displacers each in separate cylinders
• • 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
  • F02G2257/00—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
  • F02G2270/00—Constructional features
  • F02G2270/30—Displacer assemblies
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
  • F02G2270/00—Constructional features
  • F02G2270/42—Displacer drives

Definitions

• the present invention relates to a thermodynamic machine, in particular of the Carnot and / or Stirling type.
• a thermodynamic machine is typically a motor, but it can also be designed to operate as a heat pump or refrigerating machine.
• the present invention is directed more particularly to substantially volumetric ma chines in which a gas is moved to alternately bring it into contact with a hot heat exchange surface and a cold heat exchange surface.
• the hot heat exchange surface is supplied with calories from an external heat source. By its contacts with exchange surfaces having successively different temperatures, the gas undergoes temperature variations, which induce pressure variations.
• a piston executes an engine time when the pressure is high and a compression time when the pressure is low.
• thermodynamic cycle performed by the machine is as close as possible to a theoretical cycle.
• the theoretical cycle successively comprises a slow isothermal compression at the temperature of the cold source, a fast adiabatic compression, a slow isothermal relaxation at the temperature of the hot source, and a rapid adiabatic expansion.
• Such a cycle has a theoretical efficiency equal to one minus the ratio between the absolute temperature of the cold source and the absolute temperature of the ' hot source.'"
• This cycleth "" has the advantage of allowing the exploitation of weak temperature differences between the hot source and the cold source.However, it is not very suitable for large temperature differences between the sources because it then requires large pressure variations, and therefore a large displacement piston.
• the theoretical cycle successively comprises isothermal compression at the temperature of the cold source, isochoric heating, isothermal expansion at the temperature of the hot source, and isochoric cooling. Since the compression and the expansion are done at a constant temperature, the heating and the cooling take place between the same two extreme temperatures, namely that of the hot source and respectively that of the cold source. This allows heating and cooling by exchanging calories in an exchanger. This is called heating and cooling by "regeneration".
• Such a cycle has an advantageous theoretical yield, equal to the difference between the absolute temperature of the hot source and the absolute temperature of the cold source, divided by the absolute temperature of the hot source. This cycle is therefore particularly suitable for exploiting large differences in temperature between the hot source and the cold source.
• the object of the present invention is thus to propose a new thermodynamic machine which reduces the impact of all or some of the aforementioned drawbacks, and / or which is capable of operating according to at least one of the actual cycles closer to the desired theoretical cycles. .
• thermodynamic machine comprising:
• An enclosure containing a working gas and having heat exchange surfaces therein;
• Mobile moving means in the chamber for moving the working gas in the chamber and successively putting the working gas in and out of contact with each of the heat exchange surfaces to achieve successive stages of a thermodynamic cycle ;
• a mechanical power unit subjected to the pressure of the working gas is characterized in that the displacement means pass successively in front of the different heat exchange surfaces a chamber containing a substantially constant amount of working gas, at least the major part of which is generally stationary with respect to the displacement means.
• Indirect coupling allows a crankshaft collecting the driving force of the mechanical power member to rotate at least transiently at a rotation speed different from that of a shaft controlling the movement of the displacement means
• the working gas instead of driving the working gas from one chamber to another for each stage of the cycle, the working gas permanently occupies a chamber which passes in front of the different heat exchange surfaces.
• the entire amount of gas present in the chamber performs a well-defined phase of its thermodynamic cycle, in connection with a well-defined heat exchange surface.
• This allows us to clearly echo the thermodynamic cycle in the machine in times much closer than in the past to those of the desired theoretical cycle.
• the cycle efficiency is therefore improved. This makes it possible to produce machines that operate efficiently under very small temperature differences, for example with less than 100 0 K difference between the hot source and the cold source.
• the substantially constant amount of gas is a constant volume.
• the chamber may be in permanent communication with a cavity of variable volume, for example a cylinder, in which the mechanical power member moves, such as a piston.
• the room itself is variable in volume.
• the mechanical power unit may be constituted by all or part of the displacement means.
• the displacement means comprise a rotor movable about an axis.
• the heat exchange surfaces can be distributed around the axis.
• the rotor drives the chamber in rotation so that it coincides successively with the different exchange surfaces.
• the displacement means comprise two faces directed substantially towards each other to delimit the chamber.
• the chamber then has for example the shape of a cell formed in the displacement means and whose open surfaces pass in front of the different heat exchange surfaces integral with the enclosure.
• the chamber may be defined by a single face of the displacement means, in particular a flat part on the lateral surface of the rotor rotating in a cylindrical chamber.
• the heat exchange surfaces may comprise heat exchange surfaces that is to say the exchange surfaces already mentioned previously connected to a hot or cold source.
• the machine may also include thermal confinement means capable of restricting the heat exchange with the working gas.
• An original idea of the invention consists in having made a Carnot-type machine in which the displacement means pass through the region of the thermal confinement means. Which are located in the main enclosure so that there is inside the enclosure at least one thermal confinement surface interposed between the exchange surfaces.
• the displacement means drive the gas from one chamber to another, then from the other chamber to the first, by passing the gas alternately in one direction and the other through a duct which is outside the main enclosure and in which are the thermal confinement means.
• thermodynamic cycle comprises at least one adiabatic variation phase of the working gas volume.
• thermodynamic cycle of Carnot includes the passage of the working gas in contact successively with the following surfaces:
• the volume change is faster while the working gas is in contact with the confinement surfaces than while the gas is in contact with the heat exchange surfaces.
• the gas in contact with the heat-carrying surfaces must perform a heat transfer whose velocity depends in particular on the thermal inertia of the materials and the exchange surfaces.
• the heat exchange surfaces may also comprise regeneration exchange surfaces interposed between the heat exchange surfaces.
• An original idea of the invention consists in having made a Stirling type machine in which the displacement means pass through the region of the regeneration means, which are in the main enclosure.
• the displacement means drive the gas from one chamber to another, then from the other chamber to the first, by passing the gas alternately in one direction and the other through a conduit which is outside the main enclosure and in which are the regeneration means.
• the regeneration and / or confinement exchange surfaces are positioned to delimit a part of the trajectory of the moving chamber moving with the displacement means.
• a machine according to the invention can be designed to operate simultaneously several identical but out of phase thermodynamic cycles so that the heating by regeneration of a cycle is supplied with calories provided by cooling the gas in another cycle, and / or that the piston compressing the gas for adiabatic heating is driven by the energy provided by the gas-relaxing piston for adiabatic cooling.
• the transfer of calories by the regeneration exchange surfaces can take place by thermal conduction, or by an intermediate circulating fluid, or by an intermediate thermal reserve which takes in steady state a desired equilibrium temperature.
• a regeneration surface may be both a heating surface in one direction of movement of the chamber and a cooling surface in the other direction of movement of the chamber. If the movement of the chamber is a continuous rotation, the regeneration exchange surfaces are specialized for heating or respectively for cooling and heat transfer means are provided between them. The transfer can take place in the direction of rotation, or in the opposite direction. It is also possible, as will be seen later in the description of an example, to advantageously combine in the same machine transfers in both directions.
• the transfer takes place from front to behind a cold heat exchange surface, and from behind to a hot heat exchange surface, relative to the direction of movement of the heat transfer medium. bedroom. From the point of view of the transfer of frigories, the directions of transfer are the opposite of those described above for calories.
• the hybrid cycle according to the invention comprises the passage of the gas in contact with the following surfaces for a motor cycle:
• the gas performs the reverse path and the volume change direction associated with each surface other than the two regenerative surfaces must also be reversed.
• the chamber is given a flattened shape whose large faces constitute the heat exchange surfaces while at least one of the small faces is constituted by a front face of the displacement means.
• the heat exchange surfaces are formed on fins forming between them individual chambers.
• the side faces of the fins are the large faces of these rooms.
• the displacement means comprise wings which pass between the fins.
• Each flat chamber has at least one narrow face formed by the front face, that is to say the anterior or posterior face relative to the direction of movement, a wing of the displacement means.
• the invention also relates to a method for transforming energy between the thermal form and the mechanical form, wherein during a thermodynamic cycle, thermal energy is taken from a working gas during isochoric cooling and supplies this thermal energy to the working gas during isochoric heating, characterized in that the isochoric cooling and / or isochoric heating is adjacent on one side to a substantially adiabatic variation in the volume of the working gas and the other a substantially isothermal variation of the volume of the working gas.
• FIG. 1 is a pressure-volume graph of a Stirling thermodynamic cycle
• FIG. 2 is the temperature-volume graph of the cycle of FIG. 1;
• FIGS. 3 to 8 are schematic representations of principle of a machine according to the invention, in six successive stages of its operating cycle;
• FIG. 9 is a mechanical diagram of the machine of FIGS. 3 to 8;
• FIG. 10 is a view similar to Figure 9 but relating to a second embodiment of the machine according to the invention.
• FIG. 11 is a schematic perspective view, partly in section, of a third embodiment of a machine according to the invention.
• FIG. 12 is a partial sectional view along XII-XII of FIG. 15, showing the enclosure and the means for moving the machine of FIG.
• FIG. 13 is a perspective view of two superposed stator plates, relating to a Stirling thermodynamic cycle, of the machine of FIG. 11;
• FIG. 14 is a partial perspective view of the displacer of the machine of Figure 11;
• FIGS. 15 to 22 diagrammatic views of the machine of FIG. 11 at eight successive stages of its operating cycle, in section transverse to the axis of rotation of the displacer, the cylinder-piston assembly being shown rotated 90 ° for illustrative purposes;
• FIG. 23 illustrates a variant for the mechanical coupling between the displacer and the crankshaft of the machine of Figure 11;
• FIG. 24 is a block diagram showing the machine of FIG. 11 operating as a motor powered by the residual heat of a steam turbine;
• FIG. 25 is a perspective view of a hybrid stator plate coupling Carnot and Stirling cycle of the machine of FIG. 11;
• FIG. 26 is a perspective view of a heat exchange surface traversed by circulation ducts
• FIG. 27 is a partial sectional view of a heat exchange surface
• FIG. 28 is a perspective view of a stator plate relating to a Carnot thermodynamic cycle, of the machine of FIG. 11;
• Figure 31 is a pressure-volume chart of a Carnot thermodynamic cycle;
• Fig. 32 is a pressure-flight chart of a hybrid thermodynamic cycle coupling Carnot and Stirling cycle;
• FIG. 33 is a temperature-volume graph of a hybrid thermodynamic cycle coupling Carnot cycle and Stirling.
• FIG. 1 represents the evolution of the pressure of the working gas when it undergoes the four successive stages of its cycle executed in the direction of the arrows, namely a compression El from a maximum volume Vl to a minimum volume V2, an isochoric heating E2 while the volume is kept at its minimum value V2, a relaxation E3 from the volume V2 to the volume Vl, and an isochoric cooling E4 while the volume is maintained at its maximum value Vl.
• FIG. 2 shows the evolution of the working gas temperature during the same Stirling cycle, always executed in the direction of the arrows.
• This graph shows that the compression El and the expansion E3 are isothermal.
• the El compression takes place at a constant low temperature Tb and the E3 expansion at a constant high temperature Th.
• Tb the temperature
• Th the temperature
• the pressure rises from P2 to P22, and during the isochoric cooling, the pressure decreases from P1 to P1.
• the area of the cycle hatched in Figure 1, is representative of the mechanical work theoretically provided by the cycle. It can be seen that for a given volume difference V1-V2, this energy is substantially proportional to the mass of gas contained in the machine.
• the filling pressure can be increased by initially inflating the working gas in the machine.
• the gas provides heat to the source with which it is in contact.
• the gas draws heat from the source with which it is in contact.
• FIG. 31 shows an example of a Carnot engine cycle.
• FIG. 31 represents the evolution of the pressure of the working gas when it undergoes the four successive stages of its cycle executed in the direction of the arrows, namely an isothermal compression E5 from a maximum volume V31 to an intermediate volume V32 , adiabatic heating E6 by compression to a minimum volume V33, an isothermal expansion E7 from volume V33 to volume V34, and adiabatic cooling E8 while the volume increases to its maximum value V31.
• FIG. 32 shows an example of a hybrid engine cycle.
• FIG. 32 shows the evolution of the pressure of the working gas when it undergoes the six successive stages of its cycle executed in the direction of the arrows, namely an isothermal compression E9 from a maximum volume V21 to an intermediate volume V22 , an isochoric heating ElO while the volume is maintained at its intermediate value V22, an adiabatic heating EIl by compression to a minimum volume V23, an isothermal expansion E12 from the volume V23 to the volume V24, an isochoric cooling E13 then that the volume is maintained at its value V24, and adiabatic cooling E14 by increasing the volume to its maximum value V21.
• Figure 33 shows the evolution of the working gas temperature during the same hybrid cycle, always executed in the direction of the arrows.
• This graph shows that the compression E9 and the expansion E12 are isothermal.
• the compression E9 takes place at a constant low temperature T1 and the expansion E12 at a constant high temperature T4.
• T1 the pressure rises from P122 to P222
• P224 the pressure decreases from P224 to P124.
• adiabatic heating the pressure rises from P222 to P223, and during adiabatic cooling, the pressure drops from P124 to P121.
• the area of the cycle, hatched in Figure 32 is representative of the mechanical work theoretically provided by the cycle. It can be seen that for a given volume difference V1-V2, this energy is substantially proportional to the mass of gas contained in the machine.
• the filling pressure can be increased by initially inflating the working gas in the machine.
• Figures 3 to 8 show six successive states of a machine according to the invention capable of executing a real Stirling thermodynamic cycle adjacent to the cycle of Figures 1 and 2.
• the machine comprises a bore 11 formed in a body 12 which constitutes an enclosure for this bore.
• the body 12 has heat exchange surfaces which follow one another along the axis 13 of the bore.
• the exchange surfaces are carried by elements, for example metal which are separated from each other by thermal insulations 15 shown by double lines between these elements, intended to minimize heat leakage between them.
• the hot heat transfer surface 14h is connected thermal with the hot source (not shown), while the cold heat-carrying surface 14b is in thermal connection with the cold source (not shown).
• the regeneration heat exchange surface 16 is in thermal connection with a fluid circuit 18 extending between a hot thermal reserve 18gh and a cold thermal reserve 18gb.
• Two pistons 19 and 21 are sealingly slidably mounted in the bore 11. They have two end faces 52, facing each other, which define between them a chamber 22 containing a working gas. The amount of working gas contained in the chamber 22 is substantially constant. In this example, the constant quantity is a constant mass.
• the pistons 19 and 21 constitute displacement means, which move in synchronism with each other so as to successively pass the chamber 22 in front of the different heat exchange surfaces 14h, 16, 14b and thus successively put the gas working in heat exchange contact with these different exchange surfaces.
• each exchange surface 14h, 16 or 14b defines all the periphery of a respective section of the bore 11. As the pistons 19 and 21 slide in the bore, their direction of movement is parallel to the exchange surfaces constituting the bore.
• the displacement means (pistons 19, 21) successively scan the exchange surfaces and in particular, particularly remarkably, the regeneration exchange surface 16.
• the chamber 22 and the amount of working gas that it contains are essentially stationary relative to the two pistons 19 and 21. That is to say, the two pistons 19 and 21, and the chamber 22 defined between them and the gas contained therein move as a single set. Admittedly, in this example, said assembly is deformable in that the pistons are at a variable distance from one another as will be seen later. But, with respect to each piston, the gas remains always on the same side of the piston, without being driven to the other side of the piston or to another chamber through a conduit. In the situation shown in Figure 3, the two pistons 19 and 21 are positioned so that the chamber 22 having its maximum volume Vl is in thermal contact with the cold heat-carrying surface 14b.
• the two pistons 19 and 21 move together in the region of the regeneration exchange surface 16, whereas the chamber 22 retains its minimum volume V2.
• the fluid is set in motion from the hot reservoir 18gh.
• the hot fluid transfers calories to the working gas through the regeneration exchange surface 16, then goes into the cold reserve 18gb. Thanks to these. calories, the gas. work proceeds gradually from its low temperature Tb to its high temperature Th. This carries out the isochoric heating step E2 of the cycle.
• the piston 19 opposite the cold heat-carrying surface 14b, which had remained substantially stationary during the expansion step, is in turn moving in the direction of the cold heat-carrying surface 14b (FIG. 8) while the chamber 22, retaining its maximum volume Vl since the end of the expansion, is placed in thermal contact with the regeneration exchange surface 16.
• the fluid is set in motion from the cold reserve 18gb, absorbs calories contained in the working gas and cools it from the high temperature Th to the low temperature Tb then goes into the hot reserve 18gh. This accomplishes the isochoric cooling step E4 of the cycle.
• the pistons 19 and 21 constitute both gas displacement means and mechanical power members subjected to the pressure of the gas to supply mechanical energy to the gas during the compression step and collect mechanical energy from the gas during the expansion step.
• FIG. 9 shows a mechanism for actuating the pistons 19 and 21, capable at the same time of transmitting the working forces of the gas.
• the pistons 19 and 21 are located between two crank link systems 23, 24 to which they are respectively coupled.
• the two crank connecting rod systems are mechanically coupled to rotate at the same speed but with a phase difference between them such that the piston 21 situated on the side of the cold heat transfer surface 14b is ahead of the other piston 19.
• the mechanical power provided by the machine is collected on a tree motor (not shown) coupled to the two crank systems cranks, for example a motor shaft secured to one of the cranks.
• the displacement means no longer comprise a single piston 120 coupled to a single crank connecting rod system 125.
• the piston 120 is in the form of a diabolo with two end bodies 119, 121 rigidly connected to each other by a rod 126 and defining between They are the chamber 22.
• the amount of constant gas contained in the chamber 22 is now a constant volume defined between two faces 152, facing each other and each belonging to one of the bodies 119, 121.
• a bore 127 forming a working chamber, communicates with the bore 11 through the lateral wall of the latter, through a passageway 128 typically located at mid axial distance between the hot heat-carrying surface 14h and the cold heat exchange surface 14b .
• a power piston 130 slides sealingly into the working bore 127 to close the latter on the side opposite the passage 128.
• the piston 130 is coupled to a power crank system 129.
• the displacer piston 120 comprises sealing flanges 131 which are sufficiently spaced apart from one another so that the chamber 22 communicates permanently with the working bore 127. However, between each of the flanges 131 and the connecting rod 126, the end bodies 119, 121 fill most of the cross section of the bore 11. This allows, as shown in Figure 10, to communicate the chamber 22 with the passage 128 while placing the vast majority of the volume of the chamber 22 in exclusive thermal contact with a heat exchange surface such as the cold heat exchange surface 14b (situation shown) or the hot heat transfer surface 14h (non represented) which is not the one where
• the crank linkage systems 125 and 129 are mechanically coupled to each other to rotate at the same speed and with appropriate angular timing relative to each other.
• This setting is such that the power piston 130 reduces the volume available for the gas in the bore 127 when the displacement piston 120 is at its stroke end where the chamber 22 is in thermal contact with the cold heat exchange surface. 14b.
• This is the situation shown in Figure 10. It has the effect of compressing the gas while it is maintained at its low temperature Tb, which achieves the isothermal compression at low temperature El already described.
• the crank linkage system 125 moves the displacement piston 120 to the thermal contact position with the regeneration exchange surface 16 and then with the hot heat exchange surface 14h while the working piston 130 remains close to its position where the available volume in the bore 127 is low, which corresponds to the isochoric heating step E2.
• the volume available in the bore 127 expands while the displacer piston 120 positions the chamber 22 in thermal contact with the hot heat exchange surface 14h. This achieves the isothermal expansion at high temperature E3.
• the isochoric cooling step E4 is carried out when the displacer piston 120 passes in front of the regeneration exchange surface 16 in the direction of the cold heat-transfer heat exchange surface 14b while the mechanical power piston 130 remains close to its position where the available volume in the bore 127 is maximum.
• the power crank system 129 which collects the mechanical power, while the overall mechanical energy supplied or. collected by the crank connecting rod system 125 actuating the displacer piston 120 is theoretically zero.
• the displacer is rotatable.
• the displacer is a rotor always rotating in the same direction in the enclosure constituting a stator.
• the machine comprises, with reference to FIG. 11, two units 201, 301 whose respective displacers 220, 320 are rigidly connected to each other by a common rotary shaft 420.
• 301 is an elementary multi-chamber machine 222, 322. Each chamber 222, 322 executes a complete thermodynamic cycle at each half-turn of the shaft 420 and displacers 220, 320. The two displacers
• the elementary machines are of the type in which the amount of constant gas contained in each chamber is a constant volume.
• Each unit 201, 301 comprises an enclosure 212, 312 in the general shape of a sealed cylindrical vessel containing the working gas.
• 212, 312 is connected by a passage 228, 328 to a respective working bore 227, 327 which is closed on the opposite side to the passage 228, 328, by a power piston 230, 330.
• the passage 228, 328 communicates with the chamber 222, 322 through a recess 221, 321 in the displacer 220, 320.
• the pistons 230, 330 are each connected by a respective connecting rod 229, 329 to a common crankshaft 429 which is coupled to the shaft
• the gear ratio is such that the shaft 420 controlling the movement of the movers rotates half as fast as the crankshaft 429 collecting the driving force of the machine.
• each working piston 230, 330 performs a complete cycle (a round trip) when the movers perform a half-turn and therefore each elementary machine has itself carried out a complete cycle.
• the gear 425 establishes an appropriate angular wedging between the movers
• phase shift of the pistons is obtained by coupling their two links 229, 329 to the same crankpin crankshaft 429, while the two cylinders 227, 327 are at
• crankshaft 429 180 ° from each other around the axis of the crankshaft 429.
• Each of the displacers 220, 320 comprises two lobes 448 each having the general shape of a cylinder sector having axis of the axis of rotation 413.
• the recess 221, 321 is preferably cylindrical axis 413.
• the number of lobes 448 in each unit is equal to the number of thermodynamic cycles per rotation of displacer.
• the lobes 448 are integral with one another, and leave the chambers 222, 322 in the space available inside the enclosure.
• the chambers 222, 322 occupy in each chamber angular positions offset about the axis 413 of an angle (180 ° in the example) which is equal to the angle to be traveled to perform a complete thermodynamic cycle .
• all the chambers of the same enclosure execute at each moment the same stage of the thermodynamic cycle. The pressure in all the chambers of the same enclosure is therefore the same.
• This preferred feature of the invention allows according to a very advantageous improvement to provide no sealing device between the displacer and the inner walls of the enclosure .
• the problems of friction and differential expansion between the displacer and the inner walls of the enclosure are greatly attenuated or eliminated.
• the entire interior of the tank constituting the enclosure is. the pressure of the chambers 222 or 322.
• the displacer is not really a piston, but rather a kind of moving body having the function, at each moment, to occupy the space where the gas must not be.
• each chamber is subdivided into a large number of superimposed annular passages 422 (FIG. 12) surrounding the axis of rotation 413 and having a shape that is flattened parallel to a plane perpendicular to the axis of rotation 413.
• the corridors 422 are separated from each other by fins 441 which extend radially towards the axis 413.
• the inner periphery 442 of the fins 441 has a small clearance with a cylindrical central core 443 of the displacer 220.
• the core 443 closes the corridors on the side radially inside.
• Each fin 441 extends 360 ° about the axis 413 and belongs to a disk-shaped stator plate 444 (see also FIG. 13).
• the stator plates are stacked on top of each other in the enclosure.
• Each plate 444 has at its periphery an annular boss 446 having a specific thickness corresponding to the desired thickness for each corridor 422.
• a flat face of each plate rests on the boss of one neighboring plates.
• the corridors have a rectangular cross section that is the same in all axial planes.
• Each of the two lobes 448 (FIG. 14) of the displacer 220 is formed of a series of flat wings 449 in the form of a disk sector extending in a plane perpendicular to the axis of rotation 413.
• the wings are fixed on the central core 443. They have in each axial plane a section whose shape and dimensions are identical, with an operating clearance, to those of the aforementioned transverse section of the corridors.
• the wings 449 have between them a free distance that is substantially equal, at a close operating level, to the thickness of the fins 441.
• the radius of the radially outer edge 451 of the wings 449 is substantially equal, with an operating clearance, to radially of the radially inner face 447 (FIG.
• each wing 449 of a lobe 448 is coplanar with a wing 449 of the other lobe.
• each wing extends over 135 ° about the axis of rotation 413, and therefore each elementary chamber 222 extends over 45 ° about the axis 413.
• Each elementary chamber 222 is delimited between two plates by a contour formed of the lateral surface of the core 443, the cylindrical inner lateral surface 447 of a boss 446, and two end faces 452 directed towards each other of two coplanar wings. 449 of the displacer 220.
• the cylindrical central core 443 also comprises an internal recess 500 in the form of a cylindrical bore of axis 413.
• the recess 500 communicates with each elementary chamber 222 by means of a respective opening 502 made through the central cylindrical core 443. At one end of the displacer 220, the recess 500 also communicates with the passage 228, 328.
• each fin 441 and the inner peripheral face 447 of each boss 446 constitute the heat exchange surfaces of the machine. They extend parallel to the direction of circular movement of the wings 449 of the displacer.
• each fin 441 is made up of thermally conductive sectors which follow one another in the circumferential direction with a regular alternation of cold 454b or hot 454h heat-transfer sectors and regeneration sectors 456ic, fc, ir, fr which will be detailed later. .
• each angular range corresponding to a thermodynamic cycle and therefore each angular range of 180 ° in the example, there is a cold heat-transfer sector 454b carrying a cold heat exchange surface 14b and a hot heat-transfer sector 454h carrying a surface of hot heat transfer 14h.
• the heat transfer sectors 454 are extended radially outwards by a thicker zone belonging to the boss 446, through which a passage 457 is provided for the passage of a cold or hot heat transfer fluid, respectively.
• each regeneration step is subdivided into two successive phases, namely an initial regeneration phase followed by a final regeneration phase.
• This particularity is concretized by the presence of two successive regeneration sectors in each regeneration zone.
• each heating regeneration zone comprises an initial heating regeneration sector 456i1 followed by a final heating regeneration sector 456fc.
• each cooling regeneration zone comprises an initial cooling regeneration sector 456ir followed by a final cooling regeneration sector 456fr.
• Each initial heating regeneration sector 456ic, situated just behind a cold heat-transfer zone 454b, and each final cooling regeneration sector 456fr, situated just in front of a cold heat-transfer sector 454b are cold regeneration sectors having in service substantially the same temperature Tgb closer to that of the cold heat transfer areas 454b than that of the hot heat transfer zones 454h.
• Tgb Tb + (Th - Tb) / 3.
• each initial cool regeneration sector 456ir, located just behind a hot coolant sector 454h, and each final heat regeneration sector 456fc, located just in front of a hot coolant sector 454h are hot regeneration sectors having substantially the same Tgh temperature is closer to that of the hot heat transfer zones 454h than to that of the cold heat transfer zones 454b.
• each coolant sector 454 extends over 45 ° around the axis of rotation 413.
• each initial regeneration sector 456ir or 456ic, or final 456fr or 456fc extends over 22.5 ° around the axis of rotation 413.
• each regeneration zone composed of an initial regeneration sector followed by a final regeneration sector extends over 45 °.
• the angular range corresponding to a thermodynamic cycle that is to say 180 ° in the example, is divided into four equal parts, respectively assigned to isothermal compression, isochoric heating by regeneration, isothermal expansion and isochoric cooling by regeneration.
• the regeneration means operate by caloric transfer, more particularly transfer by conduction, in the circumferential direction between regeneration zones providing calories (regeneration preceding a cold heat-transfer sector) and regeneration zones. consuming calories (regeneration preceding a warm heat-exchange area).
• the cold regeneration sectors 456ic, 456fr located on either side of a cold heat-transfer sector 454b are connected to each other in a single cold-conductive hoop 460gb by a cold thermal bridge 461gb which extends radially outside the cold heat sector.
• the 456ir, 456fc hot regeneration areas located on either side of a hot heat transfer area 454h are connected to each other in a single hot thermally conductive hoop 460gh by a hot thermal bridge 461gh which extends radially outside the hot heat sector.
• each heat transfer area 454 (454h or 454b) is externally straddled by an arch 460 (460gh or 460gb) comprising a pair of regeneration sectors connected by a thermal bridge.
• Each plate 444 is composed, for each angular range corresponding to a thermodynamic cycle, of two heat transfer sectors and two arches.
• the arches 460 and in particular their thermal bridge 461 (461gh or 461gb) serve as thermal reserve. It is advantageous for this thermal reserve to be relatively large so that, in operation, the temperature of the regeneration sectors is relatively stable, that is to say that the cyclic variation in temperature is low at each passage of a chamber in contact with each other. thermal with a regeneration sector. At the same time, when the arches 460 have a high thermal capacity and a high thermal conductivity, the desired equality between the temperatures of the two regeneration sectors of the arch is better achieved in operation.
• the heat transfer zones 454 (454h or 454b) must also have a good heat capacity and good thermal conductivity so that the calories are well transferred between their heat exchange surfaces 14h or 14b on the one hand and heat transfer fluids on the other hand on the other hand, with a temperature gradient as low as possible between the heat exchange surfaces and the heat transfer fluids.
• Thermal insulations 415 are provided at the separation between each heat transfer element 454 and the arch 460 which overlaps, and between adjacent arches.
• each fin consists of an alternation of cold 554b or hot 554h heat transfer sectors between which are interspersed thermal containment sectors 556.
• the movement of the displacer then causes the passage of the gas successively by a cold heat-transfer sector 554b, a thermal confinement sector 556, a heat transfer zone 554h, and a thermal confinement sector 556.
• the sectors have a substantially identical angular range of 45 °, the thermal confinement sectors are interconnected by overlapping internally each heat transfer area.
• FIGS. 28, 26 and 27 show that the heat-transfer sectors 554b, 554h are extended radially outwards by a thicker zone belonging to the boss 546, traversed in a preferred embodiment of the lights by 557e, 557s, respectively inlet and outlet for a heat transfer fluid traversing a network of channels 558 inside each heat transfer sector.
• the circulation of the heat transfer fluid inside the heat transfer sectors 554b, 554h has the advantage, compared to the circulation described in FIG. 13, of promoting the heat exchange between the coolant and the working gas.
• all the cold or respectively hot cold port sectors are thermally paralleled between an input duct constituted by the stack of lights 557e and two output ducts formed by the stacking of the pairs of exit lights. 557s. More generally, it is described the multiple heat transfer elements mounted thermally in parallel between at least one incoming coolant conduit and at least one outgoing coolant conduit.
• the fin 441 consists of an alternation in the circumferential direction of cold 654b or hot 654h heat transfer sectors between which regeneration sectors 656c, 656r and containment sectors are intercalated. 655.
• the movement of the displacer 220 successively passes the gas working in contact with a cold heat-transfer zone 654b, a heat regeneration sector 656c, a thermal containment sector 655, a hot heat-transfer sector 654h, a cooling regeneration sector 656r, and a thermal confinement sector 655.
• each sector extends over 30 ° around the axis of rotation 413.
• Each heating regeneration sector 656c is connected, with a cooling regenerator 656r, to a thermal hoop 660 which overlaps a thermal containment sector 655 and a cold heat-transfer sector 654b consecutive, or not shown a thermal containment sector 655 and a hot heat sector 654h consecutive. It is also possible, also not shown to connect all the regeneration sectors together with arches together forming a crown. As an alternative to the embodiment of Figure 13, the overlapping arches are located radially inside the overlapped sectors and no longer outside.
• the heat transfer sectors 654b, 654h are extended radially outwards by a thicker zone belonging to the boss 646, traversed by respective inlet and outlet lights 557e, 557s for a heat transfer fluid running through a network of internal channels 558 at each coolant sector, substantially like sectors 554b, 554h of Figure 28.
• each chamber 222 cooperates only with the exchange surfaces and heat transfer means of a single plate, for the sake of clarity and simplification.
• each chamber is defined between two plates and cooperates thermally with exchange surfaces and heat transfer means of these two plates.
• the rotary displacer has each time rotated 1/8 of cycle, so 1/16 of a turn, that is to say 22.5 °, with respect to the respectively preceding figure.
• each chamber 222 is still in contact with a hot heat-transfer sector 454h.
• the other half of each chamber 222 is in thermal contact with an initial 456ir cooling regeneration sector. It is at the transition between the isothermal expansion step E3 and the isochoric cooling step E4.
• the power piston 230 approaches its end of the race, called “bottom dead center", for which the volume of the working chamber 227 is maximum.
• the gas contained in the chamber 222 yields calories to the initial 456ir cooling regeneration sector. As indicated by the H arrows, these calories propagate through the 461hp hot thermal bridge and then into the 456fc final regeneration heating areas that wait further back for passage to the next chamber. We see that this transfer of calories is in the opposite direction of the rotation of the rotor. At the same time, by giving up calories, the gas contained in the chamber 222 begins to cool.
• each chamber 222 has come into contact with a cold heat-transfer sector 454b.
• the other half of each chamber 222 is still in thermal contact with a final cooling regeneration sector 456fr. It is at the transition between the isochoric cooling step E4 and the isothermal compression step El.
• the power piston 230 begins to leave its bottom dead center.
• the gas contained in the chamber 222 yields calories to the final regeneration regeneration sector 456fr. As indicated by the arrows H, these calories propagate in the cold thermal bridge 461gb and then in the initial regeneration heating sectors 456ic located downstream which are waiting for the subsequent passage of a chamber. This transfer of calories is in the direction of rotation of the rotor. At the same time, by giving up calories, the gas contained in the chamber 222 completes its cooling.
• each chamber 222 one half of the angular extent of each chamber 222 is still. in contact with a cold heat-transfer area 454b.
• the other half of each chamber 222 is in thermal contact with an initial 456ic heating regeneration sector.
• the power piston 230 approaches its end of travel, called “top dead center", for which the volume of the working chamber 227 is minimal.
• the gas contained in the chamber 222 absorbs calories provided by the initial 456ic regeneration heating sector, from the bridge associated cold thermal 461gb, itself previously supplied with calories by the final 456fr cooling regeneration sector during the steps of Figures 17 and 18.
• the power piston 230 is at its top dead center while each chamber 222 is in thermal contact with an initial heating regeneration sector 456c and a final heating regeneration sector 456fc, supplied with energy. heat, respectively, by the final regenerative cooling sector 456fr located upstream and the initial cooling regeneration sector 456ir located downstream (see arrows H). This is the isochoric heating step E2.
• each chamber 222 has come into contact with a hot coolant sector 454h.
• the other half of each chamber 222 is still in thermal contact with a final heating regeneration sector 456fc.
• the power piston 230 starts to leave its top dead center.
• the gas contained in the chamber 222 takes up calories at the final heating regeneration sector 456fc, itself supplied with calories by the hot thermal bridge 461gh, and through it through the initial cooling regeneration sector located downstream.
• the thermal bridges operate a delayed heat transfer: one of the two regeneration sectors connected to each bridge receives calories from the gas when the chamber is in thermal contact with this sector, then the second sector of Regeneration receiving the calories through the bridge, restores them a little later, either further to the same room (case of a cold rollbar), or back to the next room (case of a hot rollbar).
• the operation has been described from the point of view of the transfer of calories.
• the machine can operate as a heat pump (for heating the heat transfer fluid hot) or refrigerating machine (for cooling the cold heat transfer fluid).
• it is sufficient to interchange the cold and hot heat transfer elements so that the isothermal expansion is done at low temperature and the isothermal compression at high temperature.
• the same result is obtained by not interchanging the cold and hot heat transfer elements, but by shifting the crankshaft 429 or the displacer rotor 220 by one half cycle, that is to say in the example by shifting the crankshaft. 180 ° and leaving the displacer rotor in unchanged position in each of Figures 15 to 22, or by shifting the rotor by 90 ° and leaving the crankshaft unchanged in each of Figures 15 to 22.
• the piston acts in the direction of an enlargement of the working chamber.
• the volume of the working gas increases, it is the stage of the isothermal expansion E7.
• the piston acts in the direction of rapid enlargement of the working chamber, the volume of the working gas increases rapidly. This is the adiabatic relaxation stage E8.
• the piston acts in the direction of a reduction of the working chamber. The volume of the working gas decreases, it is the stage of the isothermal compression E5.
• the piston acts in the direction of a rapid decrease of the working chamber, the volume of the working gas decreases rapidly. This is the adiabatic compression step E6.
• thermodynamic cycle described corresponds to a Carnot cycle.
• the theoretical yield of the Carnot cycle is equal to the theoretical yield of the Stirling cycle described above.
• the heat conduction transfers being inefficient at low thermal gradients between the hot source and the cold source the actual yield of the Carnot cycle can be greater than the actual efficiency of the Stirling cycle when the temperature gradient is low.
• the Carnot thermodynamic cycle can be traveled faster than the Stirling cycle because the thermal transfers of the Stirling cycle can be long.
• the Carnot cycle imposes large volume variations that are difficult to implement. For this reason the Stirling cycle is particularly favored during strong temperature gradients.
• the piston acts in the direction of an enlargement of the working chamber.
• the volume of the working gas increases, it is the stage of the isothermal expansion E12.
• the power piston 230 is substantially immobile so the volume of the working chamber is substantially constant.
• the gas contained in the chamber 222 yields calories to the cooling regeneration sector 656r.
• the working gas then drops to a temperature T2 higher than the temperature Tl of the cold heat exchange sector 654b. This is the isochoric cooling step E13.
• the piston acts in the direction of a decrease in the volume of the working chamber.
• the volume of the working gas decreases, it is the stage of the isothermal compression E9.
• the power piston 230 When the two chambers are in thermal contact with the heating regeneration sectors 656c, the power piston 230 is substantially immobile so the volume of the working chamber is substantially constant.
• the gas contained in the chamber 222 takes up calories at the cooling regeneration sector 656r.
• the working gas then rises to a temperature T3 lower than the temperature T4 of the hot heat exchange sector 654h. This is the isochore heating step ElO.
• FIG. 23 will only be described for its differences with respect to that of FIG. 11.
• a gear 472 whose gear wheels are non-circular.
• the toothed wheels are oval for, in a Stirling cycle, to increase the speed of rotation of the crankshaft 429 when the pistons 230 and 330 are in the vicinity of the middle of their stroke, and to reduce the rotational speed of the crankshaft 429. when the pistons 230, 330 are in the vicinity of their top and bottom dead spots.
• the crankshaft 429 drives the power output shaft 470 of the machine through the gear 472.
• crankshaft 429 This irregular rotation has the effect of minimizing the variations in the volume of gas during the heating and cooling steps, to make them more similar to the ideal isochoric stages of the cycle. As a result, most of the volume changes occur during compression and expansion.
• the gears may be substantially elliptical for a Carnot cycle but angularly offset in a manner adapted to the speed variations described above.
• the pinion can have a more complicated shape, by adjusting the ratio of the diameters of the gears to obtain at each instant the piston speed corresponding to the thermodynamic stage of the machine, in particular for the Carnot-Stirling cycle.
• crankshaft can be provided comprising two crank pins angularly offset by for example 30 °.
• the mechanism further comprises for each piston two connecting rods each articulated by one of its ends to a respective one of the crank pins, and by its other end to a respective end of a spreader whose central axis is articulated to the piston.
• FIG. 24 shows the implementation of a machine according to FIGS. 11 to 23 and 25 to 28 operating as a motor using, as a hot source, the cooler 473 of a steam turbine 474.
• the driving shaft 476 of the The turbine drives a power generating machine 477.
• the steam cooled in the cooler 473 is compressed by a compressor 478, heated in a boiler 479, typically heated by the heat of combustion of a fuel.
• the steam is then sent to the high pressure inlet 481 of the turbine 474.
• the vapor expands in the turbine 474 and then escapes through the low pressure outlet 483 to be sent to the steam circuit 484 of the cooler 473.
• the steam circuit 484 is in heat exchange relationship with a heat transfer circuit 486 containing a fluid whose nature and pressure are appropriate, especially given the temperature of the steam at the low pressure outlet 483 of the turbine.
• the coolant is kept in circulation by. a pump 487.
• the fluid is sent through the hot heat transfer zones 454h of the units 201 and 301 of the machine of FIGS. 11 to 23.
• the coolant passes through the lights 457, orifices 459 and conduits 458. After having passed through the hot heat transfer zones, the coolant returns to the cold inlet of the cooler 473.
• the installation further comprises a cold heat transfer circuit, passing through the cold heat transfer sectors of the units 201 and 301, and connected to a cold source such as an evaporator or a watercourse.
• a cold source such as an evaporator or a watercourse.
• the power shaft 429 of the machine according to the invention can be coupled to the motor shaft 476 of the turbine 474, to add its power to that of the rbine, or to be coupled to a another machine for producing electricity, or another payload.
• a machine according to the invention is feasible in many versions, depending on its power and the temperature of the sources in particular.
• the machine given as an example in Figures 11 to 23 and 25 to 28 is considered for large achievements, the units 201 and 301 having for example a diameter of a few meters, and an axial length of a few meters also.
• the fins 441 may have a thickness of a few millimeters, for example between 5 and 10 mm, as well as the chambers 422 and the wings 449 of the displacer rotor 220.
• the heat transfer sectors and the hoops of the stator plates may be metallic. If the temperature of the hot source is sufficiently moderate, the displacer rotor can be made of synthetic material. It is also possible to envisage a metal core 443 on which synthetic wings 449 would be fixed.
• the volume swept by the working piston with respect to the total volume of gas swept by the machine is a function of the temperatures.

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• Engineering & Computer Science (AREA)
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• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

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• 2007
  • 2007-12-05 FR FR0759590A patent/FR2924762A1/fr not_active Withdrawn
• 2008
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