WO2022271046A4 - New processes and devices for isothermal compression and expansion of gases and vapours - Google Patents
New processes and devices for isothermal compression and expansion of gases and vapours Download PDFInfo
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- WO2022271046A4 WO2022271046A4 PCT/RO2022/000007 RO2022000007W WO2022271046A4 WO 2022271046 A4 WO2022271046 A4 WO 2022271046A4 RO 2022000007 W RO2022000007 W RO 2022000007W WO 2022271046 A4 WO2022271046 A4 WO 2022271046A4
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- isothermalizer
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- 238000000034 method Methods 0.000 title claims abstract 17
- 238000007906 compression Methods 0.000 title claims abstract 13
- 230000006835 compression Effects 0.000 title claims abstract 11
- 230000008569 process Effects 0.000 title claims abstract 10
- 239000007789 gas Substances 0.000 title claims 96
- 230000009466 transformation Effects 0.000 claims abstract 13
- 238000004146 energy storage Methods 0.000 claims abstract 11
- 239000012530 fluid Substances 0.000 claims abstract 10
- 238000000844 transformation Methods 0.000 claims abstract 2
- 239000007788 liquid Substances 0.000 claims 48
- 239000002184 metal Substances 0.000 claims 18
- 238000006073 displacement reaction Methods 0.000 claims 17
- 238000001816 cooling Methods 0.000 claims 15
- 238000002485 combustion reaction Methods 0.000 claims 11
- 239000011551 heat transfer agent Substances 0.000 claims 11
- 238000010438 heat treatment Methods 0.000 claims 10
- 230000008859 change Effects 0.000 claims 8
- 239000007787 solid Substances 0.000 claims 8
- 238000003860 storage Methods 0.000 claims 8
- 238000010276 construction Methods 0.000 claims 7
- 239000003795 chemical substances by application Substances 0.000 claims 6
- 230000002572 peristaltic effect Effects 0.000 claims 5
- 238000010521 absorption reaction Methods 0.000 claims 4
- 230000009471 action Effects 0.000 claims 4
- 239000006265 aqueous foam Substances 0.000 claims 4
- 230000003247 decreasing effect Effects 0.000 claims 4
- 239000000446 fuel Substances 0.000 claims 4
- 230000007423 decrease Effects 0.000 claims 3
- 239000006260 foam Substances 0.000 claims 3
- 238000009413 insulation Methods 0.000 claims 3
- 238000007789 sealing Methods 0.000 claims 3
- 238000005507 spraying Methods 0.000 claims 3
- 230000001954 sterilising effect Effects 0.000 claims 3
- 230000033228 biological regulation Effects 0.000 claims 2
- 239000000969 carrier Substances 0.000 claims 2
- 239000002826 coolant Substances 0.000 claims 2
- 239000013529 heat transfer fluid Substances 0.000 claims 2
- 239000000203 mixture Substances 0.000 claims 2
- 230000035515 penetration Effects 0.000 claims 2
- 238000011084 recovery Methods 0.000 claims 2
- 230000001105 regulatory effect Effects 0.000 claims 2
- 239000004094 surface-active agent Substances 0.000 claims 2
- 230000032258 transport Effects 0.000 claims 2
- 230000015572 biosynthetic process Effects 0.000 claims 1
- 238000001354 calcination Methods 0.000 claims 1
- 238000004891 communication Methods 0.000 claims 1
- 230000001276 controlling effect Effects 0.000 claims 1
- 239000000110 cooling liquid Substances 0.000 claims 1
- 125000004122 cyclic group Chemical group 0.000 claims 1
- 230000005489 elastic deformation Effects 0.000 claims 1
- 239000013013 elastic material Substances 0.000 claims 1
- 238000009434 installation Methods 0.000 claims 1
- 238000005304 joining Methods 0.000 claims 1
- 239000008258 liquid foam Substances 0.000 claims 1
- 230000001050 lubricating effect Effects 0.000 claims 1
- 238000005461 lubrication Methods 0.000 claims 1
- 239000000463 material Substances 0.000 claims 1
- 244000052769 pathogen Species 0.000 claims 1
- 239000003507 refrigerant Substances 0.000 claims 1
- 238000005057 refrigeration Methods 0.000 claims 1
- 230000008929 regeneration Effects 0.000 claims 1
- 238000011069 regeneration method Methods 0.000 claims 1
- 230000002441 reversible effect Effects 0.000 claims 1
- 238000005096 rolling process Methods 0.000 claims 1
- 230000007480 spreading Effects 0.000 claims 1
- 238000003892 spreading Methods 0.000 claims 1
- 238000004659 sterilization and disinfection Methods 0.000 claims 1
- 230000001960 triggered effect Effects 0.000 claims 1
- 238000011144 upstream manufacturing Methods 0.000 claims 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/16—Filtration; Moisture separation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0005—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons
- F04B39/0022—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00 adaptations of pistons piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/06—Cooling; Heating; Prevention of freezing
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- 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
- F02G2270/70—Liquid pistons
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Apparatus For Disinfection Or Sterilisation (AREA)
Abstract
The present invention relates to a process for carrying out isothermal thermodynamic transformations of a closed enclosure, based on a path theoretically proven to be the most efficient in terms of energy efficiency, achieved by completing three steps: an isentropic temperature jump from that of the environment to that of the workplace, an isothermal transformation, at a constant temperature, based on a controlled variation of the piston speed, followed by an isentropic temperature jump in the opposite direction. The isothermal trajectory of the piston speed is obtained as a solution of the analytical equation (determined on a theoretical and experimental basis) of the thermodynamic transformation, and based on it are made appropriate actuators, or an algorithm is created for a regulator (12.4 in Fig.2), which transmits commands in real time to the actuators of the movable device 12.3, as well as the valves that control the fluid flows inside the device. The controller receives signals from various sensors (L, P) mounted inside the device (12.1). The process is the basis for the development of new devices, which are the subject of this invention: densifiers and rarefiators, heat recuperators with small temperature difference, heat engines, heat pumps, energy storage systems. The proposed densifiers and rarefiators are characterized by the presence of a "thermal sponge", device characterized by a large surface area in contact with the gas being compressed, an area that does not shrink during the compression process. The use of the devices and apparatus proposed in the invention leads to the achievement of outstanding performance for all technological processes in which compressions and expansions take place.
Claims
1. Technical process applied cyclically to the gas in a closed enclosure, during a cycle, or a limited time interval in this cycle, gas that changes its volume and/or pressure due to the action of some forces from outside the enclosure, characterized by the fact that, the gas from the enclosures is forced to perform a strictly isothermal transformation, and this type of transformation is obtained thanks to the action of some regulation systems of the actuation devices of the mobile components that generate the modifying forces, regulation systems which, through commands sent to these actuation devices, control the isothermal velocity, with which the volume of the enclosure and the pressure of the gas in the enclosure change, control whereby the difference between the average temperature of the gas in the enclosure and the average temperature of the elements with which it comes into contact remains at a rigorously constant value throughout the mentioned duration.
2. Thermodynamic machine with cyclic operation, designed for the application of the process of claim 1 , which we will call an isothermalizer, comprising:
- one or more closed enclosures provided with devices for the introduction at the beginning and evacuation at the end of each cycle of the gas in/out of the enclosure
- mobile components, with direct action on the gas state variables in the enclosures
- actuation devices for these mobile components, provided with adjustment devices in addition to which there may be other components:
- liquid and/or solid bodies introduced into the enclosure to exchange heat with the working gas
- devices for the continuous or intermittent introduction/evacuation into/from the enclosures of a liquid and/or an aqueous foam,
- devices for the introduction/evacuation of an additional gas flow rate from the enclosures, after the end of the intake phase,
- transducers for measuring the characteristics of the gas in the enclosures, of the heat transfer agent and of the machine components characterized by the fact that, during a period of time within a cycle, between the end of the intake phase and the beginning of the discharge phase, the gas in each enclosure is subjected to a strictly isothermal transformation through which it changes its pressure in a monotonically increasing manner (in which case the machine is a compressor, which we will call a densifier), or monotonically decreasing (in which case the machine is an expander, which we will call a rarefier), and this type of transformation is obtained due to the action of the regulating devices on the actuation of those mobile components (solid or liquid) of the machine that change the volume of the enclosure and the pressure of the gas in the enclosure by: changing the speed of the piston, or/and the rotation of the rotor, or/and the flow of the liquid piston, or/and changing the input and output flow of the circulated heat transfer agent, or/and the change of the input and output flow of the additional gas, correlation of all these changes being carried out in such a way that the difference between the average temperature of the gas in the enclosure and the average temperature of the elements with which it comes into contact (walls of the enclosure, elements mounted in the enclosure, the heat transfer agent, aqueous foam) remains at a value rigorously constant throughout the mentioned duration.
AMENDED SHEET (ARTICLE 19)
3. Technical procedure according to claim 1 , characterized in that, before and after the isothermal transformation that takes place in the isothermalizer enclosure at the working temperature Tiz, other thermodynamic transformations take place in the same enclosure, or outside it, whereby the average temperature of the working gas quantity is brought to the Tiz temperature, and after the isothermal transformation, the temperature of this amount of gas is changed, up to a desired temperature (Fig.1 B)
4. Isothermalizer with positive displacement according to claim 2, characterized in that the keeping of the constant average gas temperature is carried out by forcing, throughout the cycle, through the kinematic links of the constructive elements and/or through preset commands transmitted to the actuation device with variable instantaneous speed/angular velocity of the piston/rotor, a viz variation which was previously determined theoretically and/or experimentally
5. Isothermalizer according to claim 2, characterized in that the keeping of the constant average temperature is carried out with the help of movable elements operated by devices whose speed and position is imposed by an automatic controller, which throughout the cycle, receives and processes the signals received in real time, from measuring devices installed inside and outside the respective enclosure, determines the required position of the movable elements corresponding to the measured state variables and issue accordingly commands to the actuators
6. Isothermalizer according to claim 5, characterized in that the automatic adjustment device receives signals from the moving element position sensor and from the pressure sensors installed in the working room (Fig. 2)
7. Isothermalizer according to claim 5, characterized in that the automatic adjustment device receives signals from a series of temperature sensors mounted on the inner and outer surfaces, through which the isothermalizer performs heat transfer, estimates (zonal and/or total) the amount of heat given by the working gas to its ambient environment and that accumulated by the thermal sponges, as well as the heat given to the outside environment and sends commands accordingly to the actuation devices of the movable components
8. Isothermalizer according to claim 5, characterized in that the automatic adjustment device receives signals from a series of temperature, pressure, flow and position sensors mounted inside and outside the isothermalizer and outputs signals to the actuators of flow and/or pressure of the fluid heat transfer agents, in order to control, zonally and/or totally, the amount of heat exchanged by the working gas with its ambient environment, in order to obtain an isothermal transformation of the gas in its enclosure
9. Isothermalizer with solid piston according to claim 2, characterized in that the solid piston is actuated by the pressure of a liquid agent supplied by a variable flow hydraulic motor, and has a telescopic rod composed of several segments (13.3i of Fig.3a), these segments entering the kinematic chain successively, at certain values of the gas volume/pressure, changing the surface on which the working fluid pressure is exerted, and consequently, the displacement speed of the piston
10. Isothermalizer with positive displacement according to claim 2, characterized by the fact that, between the walls and the movable element of the machine, a device called thermal sponge (Fig. 4) is inserted, characterized by a variable geometry, being made of solid components whose total surface in contact with the gas in the cylinder is large and which is composed of a series of elements that, due to their elasticity, or the kinematic links between them, change their shape and/or position, depending
AMENDED SHEET (ARTICLE 19)
on the position of the piston/rotor, causing a change in the minimum volume in which this sponge can be fitted, but keeping almost unchanged the contact surface of the sponge with the gas inside the isothermalizer
11. Piston isothermalizer, with alternative displacement according to claim 10, characterized in that its thermal sponge is made up of one or more helical springs, arranged between the piston and the cylinder cover (Fig. 5), the springs can have coils with different sections and different diameters, some of the springs with a small diameter can be mounted inside the ones with a larger diameter some of the small diameter springs can be mounted inside the larger diameter ones
12. Piston isothermalizer, with alternative displacement, according to claim 10, characterized in that its thermal sponge is made up of helical springs, elastic cords, bellows and other types of elastic elements mounted between the piston and the cover (Fig. 6, Fig. 7), on which are fixed heat-absorbing flat plates, parallel to the surface of the piston
13. Alternative displacement isothermalizer according to claim 12, characterized in that, on both sides of the flat plates of its thermal sponge, fins or other vertical elements are fixed, with fixed length, or with variable length through various telescoping methods (Fig. 8)
14. Alternative displacement isothermalizer according to claim 13, characterized in that, at the periphery of the horizontal plates are mounted on their contour (5.11c, figure 8), and/or inwards, vertical short walls, to retain on the plates a certain amount of liquid, from that existing in the enclosure, or from that in the cooling/heating circuit, with the aim of reducing the dead volume and/or to remove the heat accumulated by the sponge
15. Alternative displacement isothermalizer according to claimI O, characterized in that its thermal sponge is made by alternating flat metal plates and curved, elastic metal plates (Fig. 9 and 10), plates which have, when the piston is at the top dead center (TDC), approximately the same surface, and through which perforations are made for the convective circulation of the gas in the enclosure
16. Alternative displacement isothermalizer according to claim 10, characterized in that its thermal sponge is made of horizontal flat metal plates, mounted on a mechanical structure with variable geometry, fixed between the piston and the cylinder cover, which deforms through the movement of the piston without altering the parallelism of the plates
17. Alternative displacement isothermalizer according to claim 15, characterized in that its thermal sponge (Fig.11 ) is made of flat horizontal metal plates (5.11 ), mounted on horizontal supports (5.20) fixed in foldable carry-supports (5.19) in the form of the narrow blades, the support- carriers having the two ends fixed by joints that allow tilting movements, one end of which is fixed, by means of a movable joint, to a flange (5.18) rigidly fixed to the piston, and the other end being fixed, also by a movable joint, to a pivoting arm, the pivoting arm having a guide roller (5.16) attached to it, which can run on a rail, or in a channel (5.17) in the cylinder head, the displacement of the piston leading to the pivoting of the support-carriers , accompanied by a change in the distance between the horizontal plates
18. Alternative displacement isothermalizer according to claim 15, characterized in that its thermal sponge (Fig. 12) is made of flat horizontal metal plates (5.11 ), mounted on folding supports (5.25) which are fixed in/on carry-supports made of rods, bars, pipes, or narrow blades, 5.22, 5.23, 5,24, the
AMENDED SHEET (ARTICLE 19)
whole structure having the shape of harmonics or bellows, whose height and/or width changes with the displacement of the piston.
19. Technical process by which a prior art piston compressor can be transformed into a densifier according to claim 2, thus increasing its energy efficiency, characterized in that this compressor is fitted with a thermal sponge according to claim 10, a device drive according to claims 4, or 5 and/or a cooling/lubricating system according to claim 21 , after performing a set of preparatory dimensional changes to its components, which allow these changes
20. Densifier according to claim 2, characterized in that when the pressure in the enclosure reaches a set point, an suction valve is opened for the penetration of a liquid piston, the gas in the enclosure being further compressed, then, after reaching the desired pressure, it is exhausted without changing its pressure, through this valve, if it is at the highest elevation of the enclosure, or through another valve properly located (Fig.14, Fig.15)
21. Piston isothermalizer according to claim 2, characterized by the fact that it contains an electronic processor that stops the piston periodically, at the top or the bottom dead center, for a period of time, so that the thermal sponge (alone or together with the piston) is extracted from the enclosure, in order to cool/heat it quickly, or for the purpose of temporary storage, in order to store the thermal energy it has absorbed (Fig.16)
22. Densifier/rarefier according to claim 2, characterized in that the working enclosure(s) of the machine is/are included in a cooling/heating system which also contains a variable flow and pressure pump for continuously or intermittently circulating the heat transfer agent (under liquid form, aqueous foam, or liquid mixed with surfactants) and an external heat exchanger, the introduction of the agent into the cylinder being done by free flow, or by spraying
23. Densifier/rarefier according to claim 2, characterized in that, in the configuration of the sponge, there are zones for collecting the liquid mixed with surfactant, zones where working gas is injected from the outside, at a pressure equal to or higher than that in the cylinder foam, for foam regeneration
24. Isothermalizer according to claim 22, characterized in that it has an electronic processor that stops/slows down the movement of the piston, at certain predetermined time intervals, for predetermined time durations, or set by a control system that receives signals from a set of temperature sensors, leaving in operation, at the working flow rate, or at an increased one, the cooling system and the lubrication system
25. Isothermalizer according to claim 22, characterized in that the portion of the heat transfer liquid circuit located inside the cylinder is made of one or more tubular helical springs, in the walls of which are mounted devices for spreading the heat transfer liquid inside the enclosures, springs that change their height depending on the position of the piston
26. Isothermalizer according to claims 16/17 and 22, characterized in that the portion of the heat transfer liquid circuit located inside the cylinder is mounted on/in the skeleton supporting the horizontal plate system, or on similar independent support structures specially mounted for this purpose
27. Isothermalizer with liquid piston, according to claim 2, characterized by the fact that a thermal sponge composed of horizontal plates (Fig. 17) is mounted inside the cylinder, on the whose periphery (or on a portion thereof) access paths are made for the access of the liquid agent above the previous
AMENDED SHEET (ARTICLE 19)
plate (skirts 7.3b in Fig.17), in such a way that the liquid penetrates almost simultaneously into all the spaces bounded by the horizontal plates, to create closed gas pockets, at almost equal pressures at different elevations, each such gas bag being provided with its own holes for gas inlet/outlet, thus becoming a small liquid piston compressor/expander (elementary isothermalizer)
28. Liquid piston isothermalizer, according to claims 2 and 27, characterized by the fact that it is made by alternating, in the same enclosure (Fig. 18), two types of elementary isothermalizers:
- the first type (7d from Fig.18) consists of two close horizontal plates, where the liquid comes from the main column, the compressed gas is transferred, as its pressure increases, through check valves mounted in the upper wall (7.10 from Fig.18 ) in the upper elementary isothermalizer, of the second type, where it is forced to pass through a layer of liquid with which it exchanges thermal energy, and the lower wall is equipped with check valves (7.1 1 from Fig.18) for liquid supply of sprinklers , or nozzles, from the lower elementary isothermalizer of the second type
- the second type (7c from Fig.18) consists of two more spaced horizontal plates, it does not have access to the main column of the liquid piston, it has valves mounted on the upper wall for the intake and for spraying the liquid from the isothermalizer of the first type located above his, it has valves for the gas coming from the lower elementary isothermalizer of the first type mounted on the lower wall, and in a side wall it has check valves through which the initial intake and final exhaust of the working gas is made
29. Liquid piston isothermalizer with vertical cylinder, according to claim 2, characterized in that, in the upper part of the cylinder, a non-deformable thermal sponge is mounted, with a large absorption surface (5gs from Fig. 21 ), and in the lower part a deformable thermal sponge, in -a first stage, a solid piston compresses the gas and reduces the volume of the deformable sponge, and in the second stage, when the piston reaches a certain position, one or more valves are opened in the piston (5.2s), allowing the penetration of a liquid agent , which still functions as a piston and as a cooling agent of the upper thermal sponge (Fig.21 and 22)
30. Liquid piston isothermalizer with vertical cylinder, according to claim 2, characterized in that, in the upper part of its cylinder, a thermal sponge (7gs from Fig. 23, 23a, 23b) with a large absorption surface is mounted, separated from the lower part by a wall (7.2s) in which a valve is mounted that allows the opening, on external command, of a communication path, in this lower part being mounted one or more thermal sponges (7g) with a high capacity of elastic deformation, made of plates elastic metal, with corrugations of different radii of curvature, or elastic metal plates rolled in the form of rolls of variable diameter, or of strips and other small elastic elements, placed in sealed deformable bags (7.14), together with a liquid fraction that removes the dead volume of these bags when fully compressed, the inflatable bags being each provided with a lower opening through which they can communicate with the layer of liquid, the opening being closed by an externally controlled valve and with an upper hole (7.2o) through which each bag communicates, also through valves, with the upper part of the cylinder, the isothermalizer operating in the first phase by moving the liquid piston until the gas is discharged from the inflatable bags, and in the second phase, after equalization at external order of the pressures in the two enclosures and the recovery of the mechanical energy stored in the elastic elements of the thermal sponges, by further moving the liquid piston
AMENDED SHEET (ARTICLE 19)
31. Liquid piston isothermalizer according to claim 30, characterized in that the deformable bags in the lower compartment contain vertical metal plates with different radii of curvature, which when subjected to external pressure created by the liquid piston, flatten to the point of overlap.
32. Liquid piston isothermalizer with vertical cylinder, according to claim 30, characterized in that a single bag, or a series of bags in the form of mattresses or tubes is mounted in the lower compartment (Fig. 23a), the bags being filled with a mixture of elastic and inelastic elements, so that in the free state it occupies most of the volume of this compartment, and when the pressure is maximum it occupies as little of this volume as possible.
33. Liquid piston isothermalizer with vertical cylinder, according to claim 2, characterized by the fact that a sponge with a large heat absorption surface is mounted in its cylinder in the upper part (7gs from Fig. 24), and in the lower one a thermal sponge in the form of a tubular pipe (7.16) with double walls, in which sprinklers are mounted, and the liquid piston of the isothermalizer circulates through the double wall of the pipe, from where a part penetrates both into the gas layer from inside the tube, as well as in the space between the pipe and the cylinder walls, the other part entering, together with the excess liquid evacuated from the enclosure, into the pipes of a loop cooling circuit
34. Liquid piston isothermalizer with a vertical cylinder, according to claim 1 , characterized by the fact that in its cylinder are mounted (Fig. 24a), a sponge with a large heat absorption surface (7gs from Fig. 24a), in the upper part, and in the lower one, thermal sponges made of concentric vertical cylinders (7.3v), arranged at greater distances in the central part of the densifier, but increasingly closer towards its periphery, fixed alternately on the upper wall and on the lower part of the device, in such a way as to create for the liquid piston that enters the cylinder through the central area, a path as long as possible, the sponge plates being provided with holes (7.3o) made in the upper part of the vertical plates to maintain the same pressure throughout the cylinder and with other holes made at lower elevations, to accentuate upward convective currents
35. Isothermalizer according to claim 1 , hereinafter called a gas piston isothermalizer, characterized by the fact that it is composed of a first stage consisting of one or more solid or liquid piston compressors/expanders, and a second stage, consisting of from a reservoir (8.2i from Fig.25) equipped with a thermal sponge cooled/heated in continuous flow, with a volume significantly larger than that of first-stage compressors, a reservoir in which the difference between the temperature of the gas and that of the heat transfer agent (and , by default, of the sponge) is maintained at a constant value by adjusting the coolant flow rate and and the flow rate of the gas from/to the first stage, the tank gas pressure increasing/decreasing with each cycle of the first stage
36. Gas piston isothermalizer, according to claim 35, characterized in that its first stage is composed of a quasi-isentropic compressor/expander (C in Fig. 26), which discharges/suctions the working gas into/from a tank with constant pressure pi, compressed gas with constant temperature Tiz, from where it is taken/where it is discharged by one or more isothermalizers, which discharge/absorb the gas to/from the second stage, where the gas temperature is maintained at the constant Tiz value and the pressure has the variable value pr
37. Gas piston isothermalizer, according to claim 35, characterized in that its first stage consists of two isentropic compressors/expanders (C1 and C3 in Fig.25) which together would ensure the
AMENDED SHEET (ARTICLE 19)
increase/decrease of the gas temperature from the value Tamb/Tiz to the value Tiz/Tamb and an increase/decrease in pressure from the value pg/pr to the value pr/p0 (where pr is the gas pressure of the second stage), between the two compressors/ expanders being an isothermalizer interposed, of whose valves are controlled by an automatic system, system which, based on the pressure signal from the second stage, ensures at the entrance/exit to/from the second isentropic compressor/expander, that pressure that ensures at its exit/entrance, an equal pressure with the pressure at that moment from the second stage
38. Gas piston isothermalizer, according to claim 35, characterized in that the tank of second stage (8.2i of Fig.25, Fig.26), together with its thermal sponge and its cooling/heating system, is inserted into a tank (8.2 from Fig.25) of larger dimensions, which in its lower part contains a heat transfer liquid, and in its upper part, above the level of the inner tank (8.2i), contains a working gas layer, which communicates through a pipe with the gas from the inner tank, as well as a thermal sponge (8gs from Fig.25) for cooling/heating this upper gas bag, the liquid from the main tank (8.2) being transported, keeping a constant level in the tank 8.2 , by a hydraulic pump, through an heat exchanger (HE)
39. Gas piston isothermalizer, according to claim 38, characterized in that the gas in the inner tank (8.2i of Fig.26) is cooled/heated by a system composed of a deformable metal band running on a roller system mounted in the main tank (8.2 of Fig.26) at the boundary between the two tanks, or in both tanks (Fig.26A), in such a way that the metal band transports thermal energy between the gas in the inner tank and the liquid in the main tank, the openings through which the band passes from one tank to the other being sealed as well as possible and the fluid level in the inner tank being maintained constant, at the lowest possible level, with the help of a pump
40. Gas piston isothermalizer, according to claim 35, characterized in that the second stage of the transformation takes place in a reservoir (8.2i of Fig.27) which is, at the same time, the primary of a plate heat exchanger, and the secondary of the exchanger contains a fluid that absorbs thermal energy from the primary and transports it to another heat exchanger, where it gives it to another medium, or it contains a refrigerant with vapor at the saturation limit, in which case this secondary becomes the evaporator/condenser of a heat pump
41. Gas piston isothermalizer, according to claim 35, characterized by being composed of two isothermal transformation systems, each with an isothermalizer (8.1 din Fig.28) and an tank(8.2i) with its own cooling/heating system (Fig.28), the two (8.2i) tanks together constituting a heat exchanger
42. Gas piston isothermalizer, according to claim 35, characterized in that its second stage (tank 8.2 of Fig.29) contains a thermal sponge composed of closely spaced vertical plates or/and of thin, deformable metal wires, which is cooled/heated by a (8.8a) sprinkler system and/or a foam generator system (8.9), the liquid accumulated at the bottom of the tank being kept at a constant level by means of a pump (8.6) which discharges this liquid through a cooling/heating system containing a heat exchanger and one or more coolersheaters with bubbles or with gas layers, gas originating from the first compression/expantion stage
43. Rotary isothermalizer, according to claim 1 , characterized by having the same construction as a rotary compressor, or a rotary pump of the state of the art for which, additional sealing measures between gas enclosures with pressure differences between them are taken and to which is attached a
AMENDED SHEET (ARTICLE 19)
controlled heat transfer system between the gas enclosure and its environment and/or which is operated by systems that enforces the isothermal angular velocity
44. Rotary isothermalizer, according to claim 43, characterized in that it is carried out on the configuration of a rotary compressor with a blade in rotor (Fig.30) to which a liquid/aqueous foam spraying system with nozzles mounted in the wall of the stator and/or rotor is attached, the fluid flow being controlled by the control valves and being also circulated through an external heat exchanger
45. Rotary isothermalizer, according to claim 43, characterized in that the liquid supplying the sprinklers is taken from a tank in which this isothermalizer is fitted
46. Rotary isothermalizer, according to claim 43, characterised by the fact that a thermal sponge consisting of cylindrical metal sheets of different diameters, with values between the diameter of the rotor and that of the stator is installed between the rotor and the stator, each of these sheets having an opening along one of the generators, to allow the blade to move alternately, the rotor centerline being moved towards the stator centerline, in the plane containing them, with a distance equal to the combined thickness of all these sheets, without leaving any spaces for gas leaks from the high pressure area to the low pressure area (Fig.34)
47. Rotary isothermalizer, according to claim 43, characterised by the attachment to a rolling piston compressor of a thermal sponge according to claim 46, of a cooling system according to claim 44 and/or of an angular velocity control system (fig.36)
48. Rotary Isothermalizer, according to claim 43, characterized by the fact that it is realized by attaching to a rotor vane compressor a cooling/heating system according to claim 44 (Fig.37) and a system adjusting the angular velocity and heat transfer fluid flows, so as to obtain the isothermal trajectory
49. Rotary isothermalizer, according to claim 48, characterized in that in the rotor of the apparatus, cavities are made in the space between the blades, where pipes equipped with sprinklers and other elements of a solid thermal sponge are fitted (Fig.38 and Fig.39)
50. Rotary isothermalizer, according to claim 43, characterized by the fact that in the pipe through which the compressed gas is discharged, mounted at the highest level of the device (Fig. 39), a layer of liquid is permanently kept, through which it is removed, in the time of discharge, the dead volume of the apparatus and through which the pressures of the gas in the apparatus and of the gas in the upstream device (e.g. a storage tank) are equalized
51. Double-effect piston isothermalizer, according to claim 2, characterized by being made by joining two isothermalizers according to claims 16, 20 and 29 in the same cylinder (Fig.40), and their common piston is operated by means of profiled cams (6.14) fitted in one of the enclosures, by means of springs (6.16) mounted in the other enclosure and by means of telescopic carry-supports (5.22, 5.23, 5.24) mounted in both enclosures
52. Rotary isothermalizer according to claim 43, characterized by having the same construction as any gear pump (Fig.41 A), to which a controlled heat transfer system between the gas in the enclosure and its environment is attached and to which it applies technical procedure in claim 50
AMENDED SHEET (ARTICLE 19)
53. Rotary isothermalizer according to claim 43, characterized by having the same construction as any cam pump (Fig.41 B), to which a controlled heat transfer system between the gas in the enclosure and its environment is attached and to which it applies technical procedure in claim 50
54. Rotary isothermalizer according to claim 43, which has the same construction as any state-of-the- art liquid ring compressor, characterized in that thermal sponges are mounted in the spaces between the rotor blades.
55. Rotary isothermalizer according to claim 43, which has the same construction as any state-of-the- art screw compressor (Fig.42A), characterized in that a thermal sponge is inserted between its spirals (6.18 and 6.19 in Fig.42A), consisting of rectangular metal plates (6.21 in Fig.42A), of a width equal to or less than the height of the main spirals and of a length approximately equal to that of these spirals, which in the unstressed state have the same shape and the same radii of curvature as the main spirals, which are supported on the fixed spirals cover and are spaced apart by rectangular elastic metal slats, with the same width as the main spirals and with a much shorter length (6.20 in Fig.42C), made and arranged in such a way that in all cross sections perpendicular to the spirals, in which the distance between the main spirals is minimal, occupy all the free space between the spirals, forming a sealing plug which separates watertight the compressor regions with different pressures as well as a controlled system for heat transfer between the gas inside the appliance and its environment
56. Isothermalizer according to claim 43, characterized in that it has the same construction as a peristaltic compressor (Fig. 42D), in which, in the peristaltic tube(s) constructed of deformable and at the same time elastic materials, a thermal sponge formed of rectangular metal plates is introduced, this metal plates being rectangular in shape, slightly wider than the diameter of the tube not deformed and the length approximately equal to that of the tube, metal plates which, in the unstressed state, have the same radius of curvature as the peristaltic tube support (6.21 in Fig.42C, or 5.14 in Fig.42E) and are spaced by elastic springs, or by rectangular elastic metal slats, with the width equal to that of the main plates and much smaller in length (6.20 in Fig.42C), made and arranged in such a way that in the cross-section from the position in which they are tensioned by the peristaltic roller to occupy the whole area of the section of the peristaltic tube, forming a sealing plug which separates watertight the two compressor regions with different pressures, the system being provided with a controlled heat transfer system between the gas inside the apparatus and its environment
57. Isothermalizer according to claim 2, characterized in that it has the same construction as a diaphragm compressor (Fig. 13), in whose enclosure a thermal sponge consisting of elastic elements or a mechanically deformable assembly are inserted, and which is provided with a controlled system heat transfer between the gas inside the appliance and its environment
58. A method of adjusting the operating characteristics of thermal engines, of refrigeration systems, of energy storage facilities, of liquefaction facilities and other types of facilities which have in structure isothermalizers according to claim 2, characterized in that it uses controllers and other devices to change during operation, the “isothermal velocities” and compression/expansion ratios of compressors and expaders in the composition
59. Method for the increase efficiency of state-of-the-art internal combustion engines, operating after a closed or open cycle, characterized in that the first phase of this cycle is an isothermal compression at
AMENDED SHEET (ARTICLE 19)
minimum cycle temperature (usually equal to atmospheric temperature), performed by a densifier according to claim 2, which replaces those phases of these cycles, in which the thermal energy of the gas in the system is released to the environment at temperatures above the minimum temperature, without modifying the other phases (Fig.43D)
60. Internal combustion engine according to claim 59, characterized in that it is composed of a densifier according to claim 2, an adiabatic compressor with an adjustable compression ratio, a combustion chamber which is at the same time an expander and in which the compressed air from downstream apparatus is heated, which use any type of fuel and in which the useful volume varies by the displacement of a movable piston, displacement which takes place during combustion, the products of combustion being introduced into a turbine (or other type of expander), by moving the combustion chamber piston in the opposite direction, at the outlet of the turbine the gases having the pressure and temperature close to the atmospheric ones (Fig.43E)
61. A quasi-isothermal combustion chamber for internal combustion engines according to claim 59, characterized in that it is located in the cylinder of a piston expander (Fig.43F), that the fuel supply starts since the gas suction phase and lasts throughout the displacement of the piston to TDC, the combustion is triggered immediately after the suction valve (drawer) is closed and the combustion continues throughout the fuel intake, and the fuel flow and piston speed are regulated by a controller to achieve an isothermal expansion.
62. Energy storage system, characterized in that it is performed using isothermal densifiers and rarefiers according to claim 1 , together with polytropic compressors and expanders, heat exchangers and/or other thermodynamic devices from the state of the art.
63. Energy storage system according to claim 62, characterized in that the mechanical energy available at a certain time is used for adiabatic compression (Fig.45B) of a working gas (which can even be the atmospheric air), after which the compressed gas is brought to the storage temperature (which can even be the atmospheric temperature) in a heat exchanger and stored in a tank under constant pressure, while the heat transfer agent that took over the thermal energy difference is stored in a thermally insulated tank, for as when an energy demand arises, the compressed gas to be expanded in a isothermal rarefier Riz1 , and the stored thermal energy is extracted with a heat engine, equipped with isothermal densifiers and rarefiers, whose hot source is the stored agent (whose temperature decreases progressively) and the cold source is the environment, or a reservoir from which the Riz1 isothermal rarefier draws its energy necessary for expansion
64. Energy storage system according to claim 63, characterized in that the compression process in the storage phase consists of three distinct steps (Fig.47): an isentropic compression from ambient temperature to a temperature T^Tn+AT, where 7); is the thermal sponge temperature at that time, an isothermal compression in a densifier at the temperature Tiz and an isentropic compression from the temperature 7^ to the maximum temperature Tm (from the heat exchanger entrance)
65. Energy storage system according to claim 62, characterized in that the available energy is taken up by a hybrid system operating after a reversed Carnot cycle, or an equivalent one (Stirling, Ericsson) (Fig. 48), which consumes this energy to transfer heat from the tank Rr to the tank Rd, in which the isothermalers D.iz and R.iz are immersed, progressively increasing the temperature and pressure
AMENDED SHEET (ARTICLE 19)
90 differences with respect to the ambient environment of the gas in the two isothermalizers D.iz and R.iz, as well as the temperature differences with respect to the ambient environment of all the elements that make up the devices in the system, of the heat transfer materials stored in the system tanks and of the gas in the tanks R5, R6 (when they exist) that store the thermal energy recovered by the Rec layers of active insulation of the Rr and Rd tanks and of the additional tanks that store the heat transfer agent R1 , R2, R3 and R4, process that results in the formation of two finite sources of thermal energy, one hot, the other cold, sources that will be used at the time of an external demand for mechanical energy, by the hybrid system that reverses its sense of operation, becoming a thermal engine that it produces mechanical energy by going through the processes of the storage phase in the opposite direction
66. Energy storage system according to claim 62, characterized in that it is composed of:
- a storage tank R under constant pressure (Fig. 49)
- a mechanical energy storage loop, which in turn is composed of a densifier D.iz2 mounted in an Rr tank with heat transfer agent with Tiz2 temperature kept constant, an adiabatic compressor C2 and an adiabatic expander T2, which ensures the temperature jump of the aspirated gas from the ambient temperature to the isothermal compression temperature Ta2 and vice versa,
- an thermal energy storage loop, which in turn consists of a heat pump with rarefier R.izp mounted in the same tank Rr and with the densifier D.izp mounted in another tank Rd with heat transfer agent with temperature Tiz1 , variable in increasing direction, from ambient temperature to maximum and an adiabatic compressor Cp and an adiabatic expander Tp,
- a mechanical power supply loop composed of a rarefier R.izf mounted in the Rd tank, an adiabatic compressor C1 and an adiabatic expander T1 , which starts in the recovery phase, to expand at the Tiz1 temperature, variable in decreasing direction the gas of tank R, until full use of the thermal energy stored in the tank Rd.
67. Energy storage system for small applications according to claim 62, characterized in that it is composed of a single reversible isothermalizer (with one or more stages) coupled with one or more tanks under constant pressure, as well from tanks for hydraulic fluid, coupled to a hydraulic pump/motor, of a system for controlling the gas temperature in the storage tanks and possibly of an electric generator to introduce the excess energy into the network
68. Method for thermal insulation of izothermalizers according to claims 2, tanks and combustion chambers according to claims 60, 61 , energy storage systems according to claim 62 and other devices of the state of the art, characterized in that the insulation layers are arranged around the apparatus in such a way as to form a circulation channel for a heat transfer fluid (Fig.44), consisting of successive layers of fluid with progressively increasing/decreasing temperature, from the environment to the surface of the device, which takes up most of the heat emitted by the device and introduces it in a series of useful applications
69. HVAC system, characterized in that it is made by using isothermal densifiers and rarefiers according to claim 2 together with polytropic compressors and expanders, heat exchangers and/or other thermodynamic devices
70. HVAC system according to claim 69, characterized in that its treatment system contains a “calcinater” (burner), in which sterilization is achieved thermodynamically by compressing air in a
AMENDED SHEET (ARTICLE 19)
91 positive displacement adiabatic compressor to a temperature above the calcination temperature of the pathogens, followed by of short standing and an energy-recovering adiabatic expansion (Fig.50A, B)
71. A system for sterilizing and cooling/heating air in one or more enclosures according to claim 69, characterized in that it consists of two interconnected loops (Fig.50C, Fig.50D), one for air, the other for exhaust working gas, one working in Carnot cycle, the other working in reversed Carnot cycle
72. System for sterilizing and cooling/heating the air in one or more enclosures, according to claim 69, as well as for other purposes, characterized in that the intake and exhaust of gases and liquids from thermodynamic machines is made through wide openings which may have a section equal to that of the cylinder of the respective device (Fig.51 A), holes that are opened and closed by switching a multiway valve and in the valve body can be created enclosures for temporary storage of fluid
73. Isothermalizer according to claim 2, characterized in that the gas is admitted and discharged from the apparatus by a 3-way valve according to claim 72 (Fig. 51 B), and the compressed gas is introduced into a cavity in the valve ball, and its exhaust is carried out by the hydraulic fluid in the discharge pipe, pipe which is directly connected to the constant pressure gas tank
74. A system for cooling or heating the air inside an enclosure, according to claim 71 , characterized in that the working gas loop operates in a Stirling cycle (Fig. 52).
75. Gas liquefaction systems, characterized in that it is made using isothermal densifiers and rarefiers according to claim 2, together with polytropic compressors and expanders, heat exchangers and/or other thermodynamic devices
76. System for gas liquefaction according to claim 75, characterized in that it works according to a Siemens cycle, the liquefied gas being sucked in and isothermally compressed (curve 1 -2 in Fig .53), in a Diz1 densifier (Fig.54), up to a pressure P2 that corresponds to an entropy s2, slightly higher than the entropy of the critical point, then, the gas is expanded adiabatically (curve 2-3 in Fig.53), in a turbine T, up to a pressure below the saturation curve of of vapors, close to the atmospheric pressure Pa and at a temperature below the critical point, the discharge being done in a condenser where, by extracting the latent heat with a heat pump (curve 3-4 in Fig.53), the gas is completely liquefied.
77. System for the liquefaction of gases according to claim 76, characterized in that the condenser of the installation is the secondary 15.21 of a plate heat exchanger, through whose primary 15.22 circulates a heat transfer agent, recirculated by a pump 15.27 through a tank 15.25 in which the Riz2 rarefier is mounted, a heat pump operating in a Carnot cycle (curve 2'-5'-4'-3' in Fig .53), or similar, and the densifier Diz2 of this heat pump pumps the heat extracted as well as that originating from the mechanical work consumed, to another heat agent, at the ambient temperature, or at a temperature different from it, the liquefaction flow control being performed by an additional system for cooling the gas in the condenser, composed of a Diz3 compressor, which uses the liquefied gas itself as a cooling liquid and an expansion valve
AMENDED SHEET (ARTICLE 19)
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