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
• • 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
  • F02G2244/00—Machines having two pistons
  • F02G2244/50—Double acting piston machines

Definitions

• the invention relates to a method and a machine which allow the realization of a quasi-isothermal compression or expansion process, that is to say a process in which the temperature of the working agent remains almost constant in undergoing practically unimportant variations, throughout the duration of the compression or expansion process, in any thermodynamic cycle, which contains such transformations.
• the method eliminates the disadvantages mentioned above, by the fact that, in order to carry out certain transformations, as close as possible to an isothermal theoretical transformation, as well as maintaining a ratio compression or expansion as high as possible, the volume of the heat exchangers does not add to the volume of the dead space determined by the constructive parameters of the variable volume chamber, since for this purpose heat exchangers are used independent of each other, in each exchanger the working agent circulating intermittently and in a single direction, exchangers which are connected and disconnected successively and cyclically with the variable volume of the working chamber, the duration of connection between this working chamber and one of the independent exchangers having two phases, in particular: in the compression isotherm, in the first phase, there is a flow of the working agent garlic from an independent heat exchanger cooled in a variable volume working chamber, until the pressures in the two volumes are equalized, the mixing process being polytropic, the working agent of the chamber transferring the heat to the working agent from the exchanger, and in the second phase there is a flow of the
• the rotary machine in accordance with the present invention, eliminates the disadvantages mentioned above, by the fact that for the purpose of carrying out the process presented above it uses groups of independent heat exchangers, i.e. -to say a group of cooled exchangers for the compression phase and a group of heated exchangers for the expansion phase *, the successive connection and disconnection between these exchangers and the working chamber of variable volume of the machine being carried out by through certain connection orifices, certain galleries, and pairs of windows made in two distribution discs and in the two fixed covers of the motor casing, windows which are arranged radially and sealed along a trapezoidal contour with expandable linear segments and certain pipes which are the same connections of the exchangers, a window ensuring the connection of the working chamber with the exchanger for the r realization of the first phase of the quasi-isothermal transformation process, the second window ensuring the connection for the realization of the second phase of the quasi-isothermal transformation process, the space between the two groups of windows corresponding to the groups of exchangers on the two covers
• the method and the machine for obtaining the quasi-isothermal transformation in the gas compression and expansion processes have the following advantages: ensures the realization of certain thermodynamic transformations as close as possible to a transformation theoretical isotherm. allows the achievement of certain high compression or expansion ratios. ensures the operation of a thermal machine with the highest yields for the same temperature difference, because it can work according to any cycle, including the Carnot cycle. allows the use of any heat source, including solar or geothermal sources and can use any type of gaseous, liquid or solid fuel. ensures the reduction of fuel consumption and reduces chemical and noise pollution. allows the operation of a thermal machine at reduced pressures and temperatures of the working agent which ensures a reduction in the stress regime and the level of wear.
• FIG. 1 Schematic diagram of the quasi-isothermal transformation process in the gas compression or expansion processes.
• fig. 2. Pressure-volume diagram of the quasi-isothermal compression and expansion processes.
• fig. 3. Temperature-entropy diagram of the quasi-isothermal compression and expansion process.
• fig. 4. Theoretical pressure-volume diagram of the cycle of a rotary external combustion engine.
• fig. 5. Longitudinal section of a rotary external combustion engine according to the invention.
• fig. 6. Motor cross section in accordance with plane II of figure 5.
• fig.7. The detail of the sealing of windows t and u. fig. 8.
• the method is applicable to any thermal machine which works with a variable volume working chamber a and provides that this chamber is successively connected and disconnected cyclically with two groups of heat exchangers. heat independent of volumes Val, Va2, Va3 ... etc. namely a group of independent cooled exchangers, of identical construction A, and a group of independent heated exchangers of identical construction B.
• Each independent cooled heat exchanger A used in the compression isotherm, is made up of certain heat exchange units 1 which have a window b for the flow of the working agent coming from the exchanger A, towards the working chamber a and a window c for the flow of the working agent coming from the working chamber a towards the heat exchanger A.
• a heated heat exchanger B used in the isotherm of expansion is formed by a heat exchange unit 2 provided with a window d for the flow of the heat agent from the working chamber a into the exchanger B and a window e for the flow of the working agent of the exchanger B in the working chamber a.
• the working chamber of variable volume a can be produced, without the example being limiting, in accordance with the block diagram of FIG. 1 on a rotary machine C, formed of a stator 3 and a rotor 4 in which the pallets slide. 5.
• the rotary machine C has a suction connection 6, and a discharge connection 7, or a discharge connection 8.
• the working chamber of variable volume a the parameters of which state initials are P O V O T O , will be connected successively in the compression phase with the heat exchangers A and in the expansion phase with the heat exchangers B via certain windows f, formed in the wall of bedroom.
• the working agent state parameters of the first heat exchanger A are P ' 1 Va 1 T " 1 .
• the duration of the connection between the variable volume chamber a and a heat exchanger A has two phases.
• the first phase in which the working agent of the heat exchanger A flows to the variable-volume working chamber a, through the window b of the exchanger A and the window f of the wall of the chamber , realizing with the working agent of the working chamber has a polytrope mixture whose state parameters are P z ⁇ , V O + V al , T z l, the working agent of the chamber yielding heat to the worker from the heat exchanger.
• the initial state values of the two gases there are the relationships:
• window b is closed simultaneously with the opening of window c and the two volumes compress together, the gas now flowing from the chamber to the exchanger through windows f and c, taking away the heat pertaining to the mass which leaves the working chamber.
• the working chamber £ detaches from the cooled heat exchanger A, is connected to the next cooled heat exchanger A, or the process is repeated exactly as at the first exchanger.
• the working agent of the heat exchanger A disconnected from the working chamber a, evolves according to an isochoric curve by exchanging heat at constant volume throughout the duration of the waiting period, until 'it will be connected to the next working chamber, which will find it at state parameters which can be considered identical with the initial parameters existing at the time of contact with the first chamber (P' 1, V al , T " 1 ) .
• the working chamber a After having traversed all the heat exchangers in number of k, the working chamber a will pass successively through the states:
• m1 the polytropic exponent of the mixture of the two gases
• m2 the polytropic exponent of the common evolution of the gas in the chamber and the exchanger
• the values P i are finished if the relationship between the volumes of the working chamber (V i ) and the volume of the independent exchanger (V ai ):
• FIGS. 2 and 3 show that the curve of the real transformations g for compression and h for relaxation are realized as a result of the addition of certain transformations sequential successive polytropes whose points of continuity i are located above and below the theoretical insothermal curve j for compression and ⁇ for relaxation.
• FIG. 3 are represented in temperature-entropy coordinates only the curves of the real transformations, that is to say the curve n for compression and the curve o for expansion.
• the process for obtaining the quasi-isothermal transformation in the processes of compression or expansion of gases can be applied to any operating cycle of any thermal machine with working chamber of variable volume and with outside heat sources such as: compressors, external combustion engines, heat pumps, refrigeration machines, etc.
• outside heat sources such as: compressors, external combustion engines, heat pumps, refrigeration machines, etc.
• the rotary external combustion engine in accordance with the present invention, consists of a rotary cylinder 9 in which slides a double-acting piston 10 provided with sealing segments 11.
• the double-acting piston 10 is mounted halfway of its length using the cousins 12 on a crank pin journal of a crankshaft 13 and for mounting reasons is formed of two halves r coupled, on the plane of separation of the cousins using the prisoners 14.
• the crankshaft 13 rests with its bearing journals g in the side covers 15 and 16 by means of bearings 17 and 18 located on the same axis.
• the rotary cylinder 9 rests on the side covers 15 and 16 using the bearings 19 and 20 which define an axis III-III perpendicular to the longitudinal axis of the cylinder, dividing it into two equal parts.
• a toothed wheel 21 with external teeth which meshes in ratio of 1: 2 a toothed wheel with internal teeth 22, integral with the rotary cylinder 9.
• a toothed wheel with internal teeth 22 integral with the rotary cylinder 9.
• In the side walls of the rotary cylinder 6 are formed four holes f communicating two by two with each room with variable volume a.
• Solid with the body of the bearings of the rotary cylinder 9 are mounted two distribution discs 23, one on each side of the rotary cylinder 9.
• the distribution discs 23 are each provided with two windows s from which galleries 24 which connect these windows s to windows f formed in the wall of the rotating cylinder 9.
• the distribution discs 23 together with the rotating cylinder 9, make the windows s pass in front of the radial windows t and u, formed in the fixed covers 15 and 16 and arranged on the same diameter as the windows s placed on the mobile distribution disks 23, t and u being sealed relative to s.
• the windows t are used for the connection of the variable-volume working chamber a to a heat exchanger A or B in the first phase by means of certain fittings 25 while the windows u are used for the connection of the same working chamber to a heat exchanger A or B in the second connection phase via the fittings 25.
• the fitting 25 constitutes the outlet fitting and the fitting 26, the inlet fitting in a heat exchange unit 1 or 2 generally known and belonging to groups of heat exchangers A or B.
• Each of the windows t and u is sealed on a trapezoidal contour with linear and expandable segments 27 mounted in generally known seats, practiced in the fixed covers 15 and 16.
• linear and expandable segments located continuously on c ⁇ untours blind trapezoids, arranged on the same diameter as the windows t and u, are also sealed the two spaces v located between the two groups of windows t and u corresponding to the groups of exchangers A and B.
• the outer covers 15 and 16 are made in the zone corresponding to the outer dead center of the piston 10 of the windows w, having the same shape and radial location as the windows t and u which are each linked with a suction connection 6. From similar to windows t and u, the windows w are sealed on a trapezoidal contour by the expandable linear segments 27.
• the suction windows w can be closed, after the engine has arrived at nominal operating speed with n ' any external control, correlated in a generally known manner, with the engine operating parameters.
• a rotary external combustion engine operates as follows. Under the action of the working gases, the double-acting piston 10 performs a transaction movement in the cylinder 9, at the same time also imposing the rotation of the crankshaft 13 and the rotary cylinder 9, around the axis III— III with a rotation speed equal to half the rotation speed of the crankshaft.
• the translational movement is purely harmonic, the maximum stroke of the piston being equal to four times the distance from the axis of the bearing journal p to the axis of the crankshaft 13, that is to say four times the eccentricity of the crankpin .
• the alignment of the toothed wheels 21 and 22 does not participate in the transmission of the engine torque to the crankshaft. Theoretically the mechanism is completely determined without this anchoring.
• the 21-22 drive double the piston-crank pin cynematic oak and has the practical role of facilitating the control of the rotation of the cylinder when the direction of the actuating forces enters under the cone of friction, without participating in transmission of engine torque.
• the mission of the angénage is consequently that of overcoming the friction forces in the rotational movement of the cylinder or of the moment of inertia, caused by the variation of the number of turns, assuming the only normal forces which could have appeared between the piston and the cylinder walls and which would have determined the rotation of the entire cylinder.
• the rotary external combustion engine in accordance with the invention, operates according to a Carnot cycle composed of two quasi-isotherms g and h which are the result of the addition of certain successive polytrope sequential transformations whose points of continuity i are found above and below the theoretical isothermal curves j and I and two adiabatic curves x and y easily obtainable by external thermal insulation, generally known, of the cylinder in the area of the working chamber.
• the Carnot cycle is carried out with an engine according to the invention, in that in the first part of the compression, the working chamber of variable volume has successively comes into contact with the cooled heat exchangers A on the path of the fittings 25 and 26, windows t and u side covers 15 and 16, window s on the distributor disk 23, galleries 24 and windows f located in the walls of the rotary cylinder 9, storing part of the agent working in these exchangers and by compressing in a quasi-isothermal manner, the rest of the working agent in accordance with the process described above.
• variable volume chamber When the variable volume chamber has left the last cooled heat exchanger A, adiabatic compression of the working agent remaining in the chamber begins, until the internal dead center of the piston.
• the motor is provided with a corresponding thermal insulation, generally known.
• variable-volume working chamber a is connected to the heated heat exchangers B, on the same path described previously, with which an exchange of working agent is obtained according to the method described , by determining the quasi-isothermal expansion of the agent remaining in the chamber.
• the work agent therein relaxes so adiabatic until the opening of the suction window w when the variable volume working chamber has reached a vacuum so that it will suck up a quantity of working agent equal to that which it has stored in the two groups of heat exchangers A and B during the previous cycle and then the cycle is repeated successively and alternately for the two working chambers a.
• the process of storing the working agent in the heat exchangers arrives, after a few dozen rotations of the crankshaft, in a stabilized state when the suction set is reduced to zero and the suction window w has to be closed. .
• the engine works with the working agent in a closed circuit.
• the mechanical work per cycle and the power of the motor increase proportionally with the increase in the suction pressure of the motor.
• the suction of the work agent can be done directly from the atmosphere or from a closed tank, in which case, the state parameters of the work agent can differ in value from the atmospheric parameters.
• the working agent can be any gas, gas mixture or heterogeneous gas-liquid mixture.
• the cooling of the heat exchangers A can be done in a known manner with any cooling agent and the heating of the heat exchangers B can be done with any heat source, including geothermal water, solar source, nuclear power or fuel burner of any type.
• thermal machine in accordance with the invention, operated as a compressor, it would be necessary to cancel, in comparison with the example presented, the group of heated heat exchangers B and the exhaust connection 7, keeping the group of exchangers of heat A and the inlet connection 6 widened and a discharge connection 8 will be used.
• a thermal machine, in accordance with the invention which would function as a compressor, could compress in a single stage the gases at relatively high ratios of compression by discharging the compressed gas at temperatures close to those of the ambient medium.
• a compressor which would operate in accordance with the invention, due to the reduced temperature of the compression space, could use synthetic materials for the construction of the piston, segments, valves, etc.
• thermal machine in accordance with the invention, operated as a heat pump or refrigeration machine, it would only be necessary to modify the arrangement of the two groups of heat exchangers so as to obtain the course of the cycle in the opposite direction than in the case of functioning as an external combustion engine.
• One group of heated heat exchangers B would be the hot source and constitute the part of the heat pump that heats, while the other group of heat exchangers A would be the cold source and would constitute the part of the refrigerating machine. which cools.
• the method and the machine for obtaining a quasi-isothermal transformation in the gas compression or expansion processes can be applied in any industrial field which supposes the need for isothermal compression or expansion , such as the chemical, refrigeration industry, etc. just like in any technical field which supposes the use of thermodynamic transformation to obtain mechanical energy, this one being able to be used in the field of transport, the production of electric energy or in other areas.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Applications Or Details Of Rotary Compressors (AREA)
• Chemical Vapour Deposition (AREA)
• Rotary Pumps (AREA)
• Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

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• 1980
  • 1980-10-08 RO RO81102311A patent/RO77965A2/ro unknown
• 1981
  • 1981-09-07 BR BR8108832A patent/BR8108832A/pt unknown
  • 1981-09-07 EP EP81902670A patent/EP0062043B1/de not_active Expired
  • 1981-09-07 JP JP56503121A patent/JPS57501789A/ja active Pending
  • 1981-09-07 US US06/387,888 patent/US4502284A/en not_active Expired - Fee Related
  • 1981-09-07 WO PCT/RO1981/000005 patent/WO1982001220A1/fr not_active Ceased
• 1982
  • 1982-06-07 SU SU823451318A patent/SU1386038A3/ru active

Non-Patent Citations (1)

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