Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B1/00—Compression machines, plants or systems with non-reversible cycle
  • F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
  • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D18/00—Small-scale combined heat and power [CHP] generation systems specially adapted for domestic heating, space heating or domestic hot-water supply
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B27/00—Machines, plants or systems, using particular sources of energy
  • F25B27/002—Machines, plants or systems, using particular sources of energy using solar energy
  • F25B27/005—Machines, plants or systems, using particular sources of energy using solar energy in compression type systems
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
  • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
  • F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
• • 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
  • F02G2250/00—Special cycles or special engines
  • F02G2250/09—Carnot cycles in general
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D2101/00—Electric generators of small-scale CHP systems
  • F24D2101/40—Photovoltaic [PV] modules
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F24—HEATING; RANGES; VENTILATING
  • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
  • F24D2101/00—Electric generators of small-scale CHP systems
  • F24D2101/70—Electric generators driven by internal combustion engines [ICE]

Definitions

• the present invention relates to an installation for the production of cold and / or heat.
• Thermodynamic machines used for the production of cold, heat or energy all refer to an ideal machine referred to as a "Carnot machine".
• An ideal Carnot machine requires a heat source and a heat sink at two different temperature levels. It is therefore a machine “ditherme”. It is called Carnot machine when it works by providing work, and Carnot machine receiving (also called Carnot heat pump) when it works while consuming work.
• the heat Q h is supplied to a working fluid G ⁇ from a hot source at the temperature T h
• the heat Q b is transferred by the working fluid Gj to a cold well at the temperature T b and the net work W is delivered by the machine.
• the heat pump mode the heat Q b is taken by the working fluid Gx at the cold source T b
• the heat Q h is transferred by the working fluid to the hot well at the temperature Tj 1 and the net work W is consumed by the machine.
• the effectiveness of a ditherme machine that is to say, an actual machine running or not as the Carnot cycle, is at most equal to that of the ideal Carnot machine and depends only on the temperatures of the source and the well.
• the practical realization of the Carnot cycle consisting of two isothermal steps (at temperatures T h and T b ) and two reversible adiabatic stages, faces several difficulties that have not been completely solved so far.
• the working fluid can remain always in the gaseous state or undergo a change of liquid / vapor state during the isothermal transformations at T h and T b .
• the performance or amplification coefficients of any trithermal or quadrithermic process are at best equal to those, denoted COPc 3 or COPc 4 or COA C3 or COA C4 , of trithermal or quadrithermic Carnot machines operating between the same temperature levels, but they are generally inferior.
• the processes for absorption, adsorption or chemical reaction of the current state of the art have efficiencies much lower than those of Carnot machines tri- or quadritherme corresponding.
• the COP 3 / COP C3 ratios are of the order of 0.3.
• the present invention is a.
• the object of the present invention is to provide a trithermal or quadritherm thermodynamic installation operating in a cycle close to the Carnot cycles, improved with respect to the installations of the prior art, that is to say an installation that operates with a change.
• liquid / vapor status of the working fluids to maintain the advantage of the small required contact surfaces, while substantially limiting the irreversibilities in the engine and receiver cycles of the tri-or quadritherme installation during the adiabatic stages, which implies better efficiencies COP / COP C or COA / COA C.
• a first object of the present invention is constituted by an installation for the production of cold and / or heat.
• a second object is constituted by a method of producing cold and / or heat using said installation.
• a trithermal or quadrithermal installation for the production of cold and / or heat, comprises a driving thermodynamic machine and a receiving thermodynamic machine, and it is characterized in that: a) the driving machine comprises on the one hand means comprising pipes and actuators for circulating a working fluid G M and secondly, in the order of circulation of said working fluid G M : an evaporator E M ; at least one transfer cylinder CT M which contains a transfer liquid LT in its lower part and the working fluid G M in the form of liquid and / or vapor above the transfer liquid; a condenser C M ; at least one device BS M for separating the liquid and vapor phases of the working fluid G M ; a device for pressurizing the working fluid G M in the liquid state; b) the receiving machine comprises on the one hand means comprising pipes and actuators for circulating a working fluid G R and on the other hand, in the order of circulation of said working fluid G R : a condenser C R ; at least one
• the cylinders CT R and CT M are connected by at least one pipe closed by actuators and in which can circulate exclusively the transfer liquid LT.
• the actuators may be valves and / or valves.
• the device for pressurizing is advantageously a hydraulic pump PH.
• the method of producing cold or heat by means of an installation consists in subjecting the working fluid G M to a succession of modified Carnot cycles in the driving machine of the installation, and it is characterized in that each cycle of the prime mover is initiated by supplying heat to the evaporator E M and initiates a modified Carnot cycle in the receiving machine by transfer of work with the aid of the transfer liquid LT, between at least a transfer cylinder of the prime mover and at least one transfer cylinder of the receiving machine.
• each evaporator is connected to a heat source and each condenser is connected to a heat sink, for example by means of heat exchangers.
• Each of the evaporators E M and E R is connected to a heat source, respectively at the temperature T hM for E M and T bR for E R.
• Each of the condensers C M and C R is connected to a heat sink, respectively at the temperature T bM for C M and T hR for C R.
• the various temperatures are such that T bM ⁇ T hM and T bR ⁇ T hR .
• eitherme modified Carnot cycle means a thermodynamic cycle comprising the stages of the Carnot cycle, engine or receiver, theoretical or similar stages with a degree of reversibility less than 100%
• quadritherme installation means an installation having the characteristics a), b) and c) above in which the temperatures T hM , T bM , T hR and T bR are different;
• trithermal installation means an installation having the characteristics a), b) and c) above in which either the temperatures T hM and T hR are identical and the temperatures T hM and T bR are different, ie the temperatures T hM and T bR are identical and the temperatures T bM and T hR are different;
• environment means any element external to the tri- or quadritherme installation as defined by characteristics a), b) and c) above. The environment includes sources and sinks of heat and possible heat exchangers;
• reversible transformation means a reversible transformation in the strict sense, as well as a quasi-reversible transformation.
• the sum of the entropy variations of the fluid that undergoes the transformation and the environment is zero during a strictly reversible transformation corresponding to the ideal case, and slightly positive during a real, quasi-reversible transformation.
• the degree of reversibility of a cycle which in practice is less than 1, can be quantified by the ratio between the efficiency (or coefficient of COP performance or COA amplification) of the cycle and that of the Carnot cycle operating between same extreme temperatures. The greater the reversibility of the cycle, the closer this ratio is to 1.
• isothermal transformation means a strictly isothermal transformation or under conditions close to the theoretical isothermal nature, knowing that, under real operating conditions, during a transformation considered as isothermally carried out cyclically, the temperature T undergoes slight variations, such as ⁇ T / T of ⁇ 10%;
• adiabatic transformation means a transformation without any exchange of heat with the environment or with heat exchanges that are sought to minimize by thermally isolating the fluid that undergoes the transformation of the environment.
• a modified motor dithermal Carnot cycle comprises the following successive transformations: an isothermal transformation with heat exchange between G M and the heat source at T h M; an adiabatic transformation with a decrease in the pressure of the working fluid G M ; an isothermal transformation with heat exchange between G M and the TbM heat sink; an adiabatic transformation with increase of the pressure of the working fluid G M -
• a modified ditherme Carnot cycle comprises the following successive transformations: an isothermal transformation with heat exchange between G R and the TW heat source; an adiabatic transformation with an increase in the pressure of the working fluid G R ; an isothermal transformation with heat exchange between G M and the heat sink at T hR ; an adiabatic transformation with reduction of the pressure of the working fluid G R.
• FIG. 1 shows a block diagram of this embodiment.
• the intended application is the production of cold temperature T bR below room temperature and / or the production of heat (with COA> 1) at temperatures T hR and T bM higher than the ambient temperature.
• Fig. 1b shows a block diagram of this embodiment.
• the intended application is the production of heat at a temperature T hR greater than those of the two heat sources at temperatures T bR and T hM (possibly identical), but with a coefficient of amplification (ratio of the heat delivered to T hR by the heat consumed at T bR and T hM ) less than unity.
• the method according to the present invention is implemented in an installation according to the present invention from an initial state in which: the engines and receiving machines are not connected to each other; in each of the machines, the actuators allowing the communication between their different constituent elements are not activated; the temperature of the entire system and in particular fluids G M and G R it contains is equal to the ambient temperature; the transfer liquid LT in the engine and receiver transfer cylinders (CT M and CT R ) are at intermediate levels between the minimum and maximum levels in these cylinders. and it includes a succession of modified Carnot cycles.
• the first cycles constitute the starting phase and they make it possible to reach the steady state.
• the successive actions carried out during each cycle of the start-up phase are the same as those of the steady state, but their effects vary progressively from one cycle to another until the steady state is obtained, in particular for values of the temperatures and pressures of the working fluids G M and G R and the temperatures of the heat transfer fluids exchanged with the heat sources and sinks.
• the first cycle of boot is constituted by a ere the step of simultaneously performing the following actions:
• the circulation of the fluids can be managed using actuators placed between the different elements of the prime mover (for the fluid G M ) or between the different elements of the receiving machine (for the fluid G R ).
• the actuators may advantageously be valves, possibly coupled to a pressing device such as for example a hydraulic pump (in particular between the device BS M and the evaporator E M of the prime mover) or an expander (in particular between the device BS R and the evaporator E R of the receiving machine.
• the level of LT is maximum in CT M, minimal in R CT, the temperature is close M G T E M hM in remaining less than T hM, and close to T bM in C M remaining greater than T bM, the temperature of R G is close to T hR in R C and R BS remaining greater than T hR and G R E R in temperature is lower than its initial temperature.
• Each cycle induces a decrease of the temperature G R in E R.
• the temperature of G R in E R reaches a value close to T bR (by lower value)
• the start-up phase is completed and the coolant is circulated in the evaporator E R , which then produces cold at the temperature T bR .
• the steady state is reached.
• the following cycles of the tri- or quadritherme installation are identical to those of the start cycles (starting from the second) except that this time all sources and heat sinks are connected.
• the starting phase of said machine is similar to the start-up phase described above, except that the transitional phase of implementation Temperature at T hr before heat transfer fluid connection concerns G R in C R.
• the working fluid G x (denoting either G R or G M ) and the transfer liquid LT are chosen such that G T is poorly soluble, preferably insoluble in LT, that G x does not react with LT and that G x in the liquid state is less dense than LT.
• G T is poorly soluble, preferably insoluble in LT
• G x does not react with LT
• G x in the liquid state is less dense than LT.
• Said means may for example consist of a flexible membrane interposed between G x and LT, said membrane creating an impermeable barrier between the two fluids but opposing only a very low resistance to the displacement of the transfer liquid and a low resistance to Thermal transfer.
• Another solution consists of a float which has a density intermediate between that of the working fluid G x in the liquid state and that of the transfer liquid LT).
• a float can constitute a great material barrier, but it is difficult to make it perfectly effective if one does not want friction on the side wall of the CT and CT 'enclosures.
• the float can constitute a very effective thermal resistance. Both solutions (membrane and float) can be combined.
• FIG. 2a shows a transfer cylinder CT containing an immiscible transfer liquid LT and an immiscible working fluid G x , LT being denser than liquid G x .
• 1 denotes the pipe allowing the exit or the entry of the transfer liquid
• 2 and 3 denote the pipes allowing the entry and exit of G x
• 4 denotes a thermal insulating coating.
• FIG. 2b shows a transfer cylinder in which LT and C x are separated by a flexible membrane 5 fixed to the upper part of the cylinder LT for example by a flange 6.
• FIG. 2c represents a transfer cylinder in which LT and G x are separated by a float 7.
• the transfer liquid LT is chosen from liquids which have a low saturation vapor pressure at the operating temperature of the installation, in order to avoid, in the absence of a separating membrane as described above, the limitations due to the diffusion of G x vapors through LT vapor at the condenser or evaporator.
• LT can be water, or a mineral or synthetic oil, preferably having a low viscosity.
• the working fluid G x undergoes transformations in the thermodynamic range of temperature and pressure, preferably compatible with the liquid-vapor equilibrium, that is to say between the melting temperature and the critical temperature. During the modified Carnot cycle, however, some of these transformations may take place in whole or in part in the domain of under-cooled liquid or superheated steam, or the supercritical domain.
• a working fluid is preferably selected from pure substances and azeotropic mixtures, to have a monovariant relationship between temperature and pressure at equilibrium liquid - vapor.
• an installation according to the invention can also operate with a non-azeotropic solution as working fluid.
• the working fluid G x may be for example water, CO 2 , or NH 3 .
• the working fluid may also be chosen from alcohols having 1 to 6 carbon atoms, the alkanes having from 1 to 18 (more particularly from 1 to 8) carbon atoms, the chlorofluoroalkanes preferably having from 1 to 15 (more especially from 1 to 10) carbon atoms, and partially or fully fluorinated or chlorinated alkanes preferably having from 1 to 15 (more particularly from 1 to 10) carbon atoms.
• 1,1,1,2-tetrafluoroethane, propane, isobutane, n-butane, cyclobutane or n-pentane may be mentioned.
• the working fluids G R and G M and the transfer liquids LT are firstly chosen as a function of the temperatures of the heat sources. and heat sinks available, as well as the maximum or minimum saturated vapor pressures desired in the machine, then according to other criteria such as in particular the toxicity, the influence for the environment, the chemical stability, and the cost.
• the fluid G T may be in the CT M or CT R chambers in the state of a biphasic liquid / vapor mixture at the end of the adiabatic expansion step for the engine modified ditherme or adiabatic compression cycle.
• the modified ditherme Carnot cycle receptor In this case the liquid phase of G x can accumulate at the interface between G ⁇ and LT.
• the vapor content of G T is high (typically between 0.95 and 1) in the CT M or CT R enclosures before the connection of said enclosures with their respective condensers C M or C R , it is possible to envisage totally eliminating the liquid phase of G x in these enclosures.
• This removal may be effected by maintaining the temperature G ⁇ working fluid in pregnant CT M or CT R at the end of the speaker communication formatting steps CT M or CT R and their respective condensers, to a value greater than that of G x working fluid in the liquid state in said condensers, so that there is no liquid in G ⁇ CT or CT R M at this instant.
• the installation comprises heat exchange means between, on the one hand, heat sources and sinks which are at different temperatures, and on the other hand evaporators, condensers and possibly the working fluid.
• G x in the CT M and CT R transfer chambers so as to eliminate any risk of condensation of G M in CT M or G R in CT R.
• FIG. 4 shows an embodiment of a transfer cyclider which allows a heat exchange.
• Said cylinder comprises a double jacket 8 in which a heat transfer fluid can circulate, with an inlet 9 and an outlet 10 for said heat transfer fluid.
• an element comprising a transfer cylinder CT M and a transfer cylinder CT R is designated “element CT M / CT R ".
• a plant according to the present invention comprises a single element M CT / CT R.
• a plant comprises two elements CT M / CT R designated by CT M / CT R and CT M '/ CT R>.
• a plant comprises two elements CT M / CT R and CT M '/ CT R>, two separate pressurizing devices designated by BS M i and BS M2 for the prime mover, and two devices pressurizing designated BS R i and BS 1 ⁇ 2 for the receiving machine.
• 5 shows an example of plant according to the basic configuration of the 1st embodiment (designated by UO), that is to say comprising a single element M element CT / CT R.
• the driving machine comprises:
• a transfer cylinder CT M containing in the lower part a transfer liquid LT, and in the upper part the driving fluid G M ;
• the receiving machine comprises:
• each of the transfer cylinders shown is thermally isolated from the environment and corresponds to Figure 2a. It could be replaced by a cylinder maintained at a temperature sufficient to prevent any condensation of G M (OR G R ) in CT M (CT R ), in the form shown in Figure 4.
• thermodynamic cycles followed by the receiver fluids G R and G M motor in the installation according to the variant UO are described in the Mollier diagram (respectively Figure 6a and 6b), which represents LnP (logarithm of the pressure) as a function of h (mass enthalpy of the fluid) and in the diagram of Clausius-Clapeyron ( Figures 6c and 6d), which gives Ln (P) as a function of (-1 / T).
• the relative position of the equilibrium lines for the fluids G R and G M in the Clausius-Clapeyron diagram differs according to whether the operating mode of the tri- or quadritherme installation is of the "HT motor / LV receiver" type (FIG. 6c) or type "HT receiver / LV motor” ( Figure 6d)
• a cycle of operation of an installation according to Figure 5 comprises four successive stages commencing respectively at the instants t ⁇ t ⁇ , ⁇ t and tg which are described below in the case of the mode "motor HT / receiver BT ".
• the description of a cycle is made for steady state operation. Unless otherwise specified, the solenoid valves are closed.
• the level of the transfer liquid LT is low (denoted B) in the cylinder CT R and high (denoted H) in the cylinder CT M and the saturation vapor pressure of the receiver and engine fluids is low and equal to P b in both cylinders. It is at this moment in the cycle that the configuration of the installation shown schematically in FIG.
• the liquid G M is sucked into the bottle BS M , discharged by the circulator in E M where it evaporates by taking heat at the hot source at T hM .
• the rate of introduction of liquid G M into the evaporator is equal to the saturated steam flow output, so that the evaporator remains always filled and keeps a constant efficiency for heat exchange.
• the saturated vapors of G M occupying a greater volume than liquid G M , the transfer liquid in the cylinder CT M is discharged downwards.
• the fluid G M follows the transformations a ⁇ b ⁇ bi ⁇ c described in FIGS. 6b and 6c.
• the transfer liquid LT in the cylinder CT R is discharged to the high level (denoted H), the saturated vapors of G R condense in C R and the condensates accumulate in BS R.
• the fluid G R follows the transformation 2 ⁇ 2i ⁇ 3 described in FIGS. 6a and 6c.
• the heat of condensation of G R is delivered at the temperature T hR .
• the subcooling of G R can be very low or even zero. If it is zero, points 2 ⁇ and 3 of Figure 6a are merged.
• the liquid G R is sucked into the bottle BS R , isenthalpically expanded through the expander D (consisting of a capillary or a needle valve) and introduced in bi-phasic form into the evaporator E R where it ends. evaporate.
• the saturated vapors of G R produced drive down (noted B) the transfer liquid in the cylinder CT R.
• the fluid G R follows the transformations 3 -> 4 -> 1 described in FIGS. 6a and 6c.
• the heat needed to the evaporation of G R is taken at low temperature T bR .
• the work W b is transferred during the transformation 4 ⁇ 1 to the motor circuit via the transfer liquid LT. at the level of the motor circuit:
• the transfer liquid LT in the cylinder CT M is forced upwards (denoted H), the saturated vapors of G M condense in C M and the condensates accumulate in BS M.
• the fluid G M follows the transformation d ⁇ a described in FIGS. 6b and 6c.
• the condensation heat of G M is delivered at the temperature T bM .
• the installation is again in the ⁇ state of the cycle.
• the heart of the invention lies during the ⁇ and ⁇ phases on the work transfer device between the motor cycle and the receiver cycle via the transfer liquid LT acting as a liquid piston.
• thermodynamic transformations followed by the fluids G R and G M and the levels of the transfer liquid LT are summarized in Table 1.
• the state of the actuators (solenoid valves and clutch of the pump PH) is summarized in Table 2, in FIG. which x means that the corresponding solenoid valve is open or that the pump PH is engaged.
• An installation which comprises two sets CT M / CT R and CT M > / CT R > and which operates according to Carnot cycles modified in opposition of phase allows moreover, by means of the addition of complementary elements, various types of recoveries of energy: according to a variant, called "UL”, energy is recovered by a receiving machine from a prime mover, via the transfer liquid LT; according to a variant, called "UG”, energy is recovered by the driving or receiving machine, via the gas phase (respectively
• G M OR G R a variant, known as "ULG" energy is recovered via the transfer liquid and via the gas phase, which constitutes a combination of UL and UG variants.
• the energy recoveries induce increases in the COP and COA of the tri- or quadritherme installation.
• the motor circuit comprises:
• the receiver circuit comprises:
• an electrovalve EV 3 between BS R and the evaporator E R the receiver circuit and the motor circuit are connected by conduits connected to the lower part of CT R , CT R >, CT M and CT M > respectively by the valves EV R , EV R > EV M , EV M 'and EV L for selectively put in communication with any two transfer cylinders.
• each of the transfer cylinders shown is thermally isolated from the environment and corresponds to FIG. 2a. It could be replaced by a cylinder maintained at a temperature sufficient to prevent any condensation of G M (or G R ) in CT M (CT R ), in the form shown in Figure 4.
• the installation shown in Figure 7 comprises a prime mover and a receiving machine operating in two cycles in opposition of phase.
• the first cycle involves the CT M and CT R transfer cylinders and the solenoid valves associated therewith.
• the cycle in phase opposition with the first cycle involves the transfer cylinders CT M 'and CT R > and the solenoid valves associated therewith.
• the other elements evaporators, condensers, separating bottles, hydraulic pump or circulator and pressure reducer are common to both cycles.
• the variant UO-OP can be implemented in an installation according to FIG. 7 in which the EV valve L is closed, or in a similar installation comprising neither the EV valve L nor the corresponding conduit. Its operation is not described here.
• the UL variant which necessarily works with two cycles in opposition of phase, brings a further improvement of the COP and COA for a minimal increase of the complexity of the installation which allows the variant UO-OP (simple addition of solenoid valve EV L ).
• the operating cycle of an installation according to FIG. 7 in the UL variant consists of 6 successive phases starting respectively at the instants t ⁇ , t ⁇ , t ⁇ , t g, t ⁇ and t ⁇ .
• the level of the transfer liquid LT is low (denoted B) in the cylinder CT R , high (denoted H) in the cylinders CT R > and CT M and intermediate (denoted I) in the CT cylinder M '-
• the saturation vapor pressure of the receiver and engine fluids is respectively low (P b ) and high (P h ) in these two cylinders CT R and CT M ' - It is at this point in the cycle that corresponds the configuration of the installation shown schematically in Figure 7.
• this intermediate pressure P m is calculated by an energy balance on the closed system consisting of the two cylinders CT R and CT M > holding account of the fluid state equation G R and G M - During this step.
• the fluid G R contained in the cylinder CT R follows the transformation l ⁇ 1 m while the fluid G M contained in the cylinder CT M > follows the transformation c ⁇ c m ( Figure 8).
• the work W L is transferred via the transfer liquid CT M > to CT R.
• the level of LT in the CT R cylinder increases to an intermediate level "I" (between levels B and H) and the level of LT in the cylinder CT M > decreases to threshold B.
• EV 2 is opened which puts in communication the cylinder CT R , the condenser C R and the separating bottle BS R in which the vapor pressure of the receiving fluid G R is equal to P h .
• the pressure in the cylinder CT R is then imposed rapidly by the liquid-vapor equilibrium of G R in the bottle BS R , the latter then performing the function of evaporator drowned.
• the heat necessary for the evaporation of G R in BS R is supplied at the temperature T hR .
• the fluid G R contained in the cylinder CT R follows the transformation l m ⁇ 2 described in FIG. 8a.
• the transfer liquid LT in the cylinder CT R is discharged from level I to level H, the saturated vapors of G R condense in C R and the condensates accumulate in BS R.
• the fluid G R follows the transformations 2 ⁇ 2i ⁇ 3 described in FIG. 8a.
• the heat of condensation of G R is delivered at the temperature T hR .
• the subcooling of G R can be very low or even zero. In the latter case the points 2 ⁇ and 3 of Figure 8a are merged.
• the installation tri- or quadritherme has completed a half cycle.
• the second half-cycle is symmetrical with the first with reversing cylinders CT M and CT M 'on the one hand and cylinders CT R and CT R > on the other hand.
• This phase is equivalent to the ⁇ phase described above (same transformations c m ⁇ d and l m ⁇ 2), but the cylinders concerned are CT R > and CT M (which implies the openings of solenoid valves EV 2 'and EVd instead of EV 2 and EVdO-
• the device comprises two elements CT M / CT R and bottles separating BS motor cycles and receiver are split.
• This variant not only allows partial energy recovery between the driving and receiving machine during the depressurization / pressurization phase (said transfer being permitted by the presence of two elements "transfer cylinder CT M / transfer cylinder CT R "), but also an additional limitation of certain irreversibilities.
• This advantage is obtained by avoiding too much subcooling of liquid G M before its introduction into the evaporator E M at high temperature and aiming at a relaxation of liquid G R closer to the isentropic transformation than the isenthalpic transformation.
• the so-called “UG” variant allows internal energy recoveries (U) within the motor or receiver circuits via the gaseous phase of the working fluids (respectively G M or G R ).
• the so-called “ULG” variant combines the two "UL” and "UG” variants.
• An installation corresponding to the 3rd embodiment and allowing UG variant or ULG variant comprises an engine as shown in Figure 9a and a receiving unit as shown in Figure 10a, the two machines are connected via the liquid LT transfer.
• a PH circulator ensuring the circulation of the fluid in the liquid state
• an electrovalve EV 6 between the other branch of TB M and the bottle BS M2 ; an electrovalve EV 3 between BS M i and BS M2 ;
• a receiving machine according to Figure 1 Oa comprises:
• the receiver circuit and the motor circuit are connected by conduits connected to the lower part of CT R , CT R >, CT M and CT M > respectively by the valves EV R , EV R -, EV M, EV M '.
• Solenoid valve EV L is used to selectively connect one of the cylinders CT M or CT M ' with one of the cylinders CT R or CT R >.
• solenoid valve EV L and the pipe on which it is installed are not useful. If they exist in the installation, solenoid valve EV L is closed.
• each transfer cylinder shown is thermally isolated from the environment and corresponds to Figure 2a. It could be replaced by a cylinder maintained at a temperature sufficient to prevent any condensation of G M (or G R ) in CT M (CT R ), in the form shown in Figure 4.
• the operating cycle of an installation according to the variant UG represented in FIGS. 9a and 10a consists of 6 successive phases beginning respectively at the instants t ⁇ , t ⁇ , t ⁇ , t ⁇ , t ⁇ and t ⁇ . .
• Table 6 indicates (by X) for each step whether the valves are open and whether the circulator PH is operating.
• the level of the transfer liquid LT is low (denoted B) in the cylinders CT R and CT M 'and high (denoted H) in the cylinders CT R > and CT M '.
• the saturation vapor pressure of the receiver fluids G R and G M engine is low (Pb) in cylinders CT R and CT M and high (Pj 1 ) in cylinders CT R > and CT M '.
• Separating bottles BS 1 ⁇ 2 and BS M2 respectively contain the fluids G R and G M in the saturated liquid state and at the same high pressure P h . It is at this moment in the cycle that the configuration of the installation shown diagrammatically in FIGS. 9a and 10a corresponds.
• Step ⁇ (between the instants U and tfc) - at the level of the motor circuit:
• the solenoid valves EV d 'and EV 6 are opened, which puts the cylinder CT M > into communication with the bottle BS M2 -
• the fluid G M follows the transformation a ⁇ a j in the bottle BS M2 , and the transformation c ⁇ C j in the cylinder CT M >.
• the high-pressure saturated vapors from CT M > partially condense in BS M2 by increasing the pressure and the temperature of G M -
• the final pressure P j is calculated from a report on energy conservation. internal of the closed and adiabatic system constituted by the two elements (BS M2 and CT M >) and taking into account the equation of state (P versus V 5 T) and the liquid-vapor equilibrium of G M.
• the solenoid valves EVi and EV 5 are opened, which puts the cylinder CT R and the bottle BS R2 into communication.
• the fluid G R follows the transformation 3 ⁇ 3j in the bottle BS R2 and the transformation 1- ⁇ 1 in the cylinder CT R.
• BS R2 some of the liquid vaporizes, which has the dual effect of lowering its temperature and raising the pressure in CT R.
• the final pressure P 1 is calculated in the same way as for P j , but with the liquid-vapor equilibrium of G R.
• the two variations of internal energy (U 3 - U 31 ) and (Ui 1 - Ui) are noted for convenience W GR in Figure 10b although it is not an exchange of work between BS R2 and CT R.
• the preceding solenoid valves are closed, except the solenoid valve EV d '.
• the solenoid valve EV b is opened and the circulator PH is actuated, which puts in communication the device BS M2 and the evaporator E M.
• the fluid GM in the saturated liquid state, is introduced into the evaporator and follows the transformation a j ⁇ b in PH, then the transformation b ⁇ bi in E M.
• the solenoid valve EV 4 is opened, which puts in communication the device BS R2 and the evaporator E R.
• the fluid G R in the saturated liquid state follows the isenthalpic transformation 3j-4 before being introduced into the evaporator E R.
• the solenoid valve EV 2 is opened, which puts in communication the cylinder CT R , the condenser C R and the bottle BS RI .
• the vapor pressure of the receiving fluid G R which was equal to P 1 in CT R increases rapidly up to the value P h imposed by the liquid-vapor equilibrium at the level of BS R i acting as an evaporator.
• the heat of evaporation is brought to T hR and the level of liquid G R contained in BS R i decreases during this step.
• the fluid G R contained in the cylinder CT R follows the transformation lj ⁇ 2.
• This step constitutes the main step of this half cycle, because it is the one during which intervene the useful heat exchanges between the installation tri- or quadritherme and the outside.
• the steps of the 2 nd half cycle are symmetrical with those of the 1 st half cycle with the only modification being a simple reversal of the CT M and CT M 'cylinders on the one hand and CT R and CT R > on the other hand (see Tables 5). and 6).
• the operating cycle of an installation according to FIGS. 9a and 10a in the ULG variant consists of 8 successive phases beginning respectively at the instants t ⁇ , t ⁇ , t ⁇ , t ⁇ , t ⁇ , t ⁇ and V
• Table 8 indicates (by X) for each step whether the valves are open and whether the PH circulator is working
• the level of the transfer liquid LT is low (denoted B) in the cylinder CT R , intermediate (denoted I) in the cylinder CT M 'and high (denoted H) in the cylinders CT R > and CT M.
• the pressure of the saturating vapors of the receiver fluids G R and G M engine is low (P b ) in cylinders CT R and CT M and high (P h ) in cylinders CT R > and CT M '.
• the bottles separators BS R2 and BS M2 respectively contain the fluids G R and G M in the saturated liquid state and at the same high pressure P 11 .
• Step ⁇ (between instants U and t ⁇ ) at the motor circuit
• the solenoid valves EV d 'and EV 6 are opened, which puts the cylinder CT M ' and the bottle BS M2 into communication with each other.
• the fluid G M follows the transformation a ⁇ a j in the bottle BS M2 and the transformation c ⁇ C j in the cylinder CT M '- the saturated high-pressure vapors coming from CT M ' condense in part in BS M2 by increasing the pressure and the temperature of G M -
• the final pressure P j is calculated from a report on the conservation of the internal energy of the closed and adiabatic system constituted by the two elements (BS M2 and CT M ') and taking into account the equation of state (P versus V, T) and the liquid-vapor equilibrium of G M.
• the solenoid valves EV 1 and EV 5 are opened, which puts the cylinder CT R and the bottle BS R2 into communication.
• the fluid G R follows the transformation 3 -> 3i in the bottle BS R2 and the transformation 1 -> 1 1 in the cylinder CT R.
• BS R2 some of the liquid vaporizes, which has the dual effect of lowering its temperature and raising the pressure in CT R.
• the final pressure P is calculated in the same way as for P j but with the liquid-vapor equilibrium of G R.
• the two variations of internal energy (U 3 - U 31 ) and (Un-Ui) are noted W GR in Figure 10c although it is not a work exchange between BS R2 and CT R.
• this intermediate pressure Pm is calculated by an energy balance on the closed system consisting of the two cylinders CTR and CTM ', taking into account the state equation of the fluids GR and GM.
• the fluid GR contained in the cylinder CTR follows the transformation li ⁇ lm while the fluid GM contained in the cylinder CTM 'follows the transformation cj ⁇ cm ( Figure 1 Oc-I Od).
• the work WL is transferred via the transfer liquid from CTM 'to CTR.
• the level of LT in the cylinder CTR increases to the intermediate level I and the level of LT in the cylinder CTM 'decreases to the threshold B.
• the previous solenoid valves are closed, the solenoid valve EV b is opened and the circulator PH is actuated, which puts the separation bottle BS M2 and the evaporator E M in communication with one another.
• the fluid G M in the saturated liquid state, is introduced into the evaporator and follows the transformation a j ⁇ b in PH, then the transformation b ⁇ bi in E M.
• the solenoid valve EV 4 is opened, which puts in communication the separating bottle BS R2 and the evaporator E R.
• the fluid G R in the saturated liquid state follows the isenthalpic transformation 3j ⁇ 4 before being introduced into the evaporator E R.
• the solenoid valves EV 2 are opened, which puts in communication the cylinder CT R , the condenser C R and the separating bottle BS R i.
• the vapor pressure of the receiving fluid G R which was equal to P m in CT R , increases rapidly up to the value P h imposed by the liquid-vapor equilibrium at the level of BS R i acting as an evaporator .
• the heat of evaporation is brought to the temperature T hR and the level of G R liquid contained in the bottle BS RI decreases during this step.
• the fluid G R contained in the cylinder CT R follows the transformation l m ⁇ 2.
• This step is the main step of this half cycle, because it is during this stage that intervene the useful heat exchanges between the modified Carnot machine tri- or quadritherme and outside.
• the transfer liquid from CT R > is pumped into the cylinder CT M ' from the low level to the high level, which corresponds to a transfer of work W b (lower in absolute value at W h ) of the receiver circuit to the motor circuit.
• the transfer liquid originating from CT M is discharged into the CT R cylinder from the intermediate level I to the high level H.
• the saturated vapors of G R condense in C R (transformation 2 ⁇ 3) and the condensates pass through the bottle BS R i then accumulate in BS ⁇ (the valve EV 3 being open).
• the heat of condensation of G R is delivered at the temperature T hR .
• the steps of the 2 nd half cycle are symmetrical with those of the 1 st half cycle with the only modification being a simple reversal of the CT M and CT M 'cylinders on the one hand and CT R and CT R > on the other hand (see Tables 7). and 8).
• the uses of an installation according to the present invention depend in particular on the temperature of the available heat sources and heat sinks and on the operating mode chosen between "HT motor / LV receiver” or "LV motor / HT receiver”.
• the temperature T hM of the hot source of the prime mover is greater than the temperature T hR of the heat sink of the receiving machine.
• the targeted applications are the production of cold temperature T bR below room temperature and / or the production of heat (with a coefficient of amplification COA 3 , ratio of the heat delivered to T hR and T bM by the heat consumed at T hM , greater than 1) at temperatures T hR and T bM greater than the ambient temperature, the temperatures T hR and T bM possibly being identical.
• this 1 operating mode with a heat consumption at T hM, to ensure freezing functions, refrigeration, air conditioning and / or heating of the habitat.
• the temperature T hM is lower than the temperature T hR .
• the intended application is the production of heat at a temperature T hR higher than those of the two heat sources at temperatures T bR and T hM (possibly identical as shown in Figure Ib), but with an amplification coefficient (ratio of the heat delivered to T hR by the heat consumed at T bR and T hM ) this time less than 1 'unit.
• This second mode of operation thus makes it possible to revaluate heats rejected at average temperatures.
• the installation can operate according to the variants UO, UO-OP, UL, UG and ULG described above.
• Embodiment of the invention for cooling the habitat using heat provided by flat solar collectors.
• the method operates according to the "HT motor / LV receiver" mode.
• working fluids 1,1,1,3,3,3-hexafluoropropane (HFC R236fa) can be used for the working fluid, and tetrafluoroethane (HFC R-134a) for the receiving fluid.
• HFC R236fa 1,1,1,3,3,3-hexafluoropropane
• HFC R-134a tetrafluoroethane
• the temperature T hM (from flat solar collectors) is equal to 65 ° C.
• the temperature T bR required for the production of cold in the evaporator E R is set at 12 ° C. This temperature is compatible with the use of a cooling floor in the house with a recommended heat transfer fluid inlet at approximately 18 ° C.
• the performance coefficients of the steady-state plant, determined by energy balance for the three variants, are as follows:
• the objective is to heat the home by using as heat primary heat provided by flat solar collectors and amplifying it by an installation operating according to the mode "motor HT / receiver BT".
• the working fluids retained are the same as in Example 1, either for the working fluid, HFC R236fa and for the receiving fluid, HFC Rl 34a.
• thermodynamic stresses are identical to those of Example 1, namely:
• the temperature T hM (from flat solar collectors) is equal to 65 ° C.
• the temperature T bR of R134a in the evaporator E R is set at 12 ° C. This temperature is compatible with a heat extraction taken at the level of a geothermal collection in winter outside the house to be heated.
• the ratio COA 4 (UL) / COA C4 is even better ( ⁇ 80%).
• the same installation according to the invention can provide the cooling functions in summer (examples 1 and 2) and heating (with amplification) in winter (the present example 3) with excellent performance in COP and COA compared to the current state of the art.
• the working fluids retained are for the working fluid, HC n-pentane and for the receiving fluid, water.
• the ratio COA 3 (UL) / COAC 3 is also very good ( ⁇ 48%).
• heat pump mechanical vapor compression

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