mechanical-liquid piston heat pumps

Abstract

GROUPED MECHANO-LIQUID PISTON HEAT PUMP The grouped mechano-liquid piston heat pump (1) comprises a blind liquid cylinder of compressors (8) in which a double-acting hydraulic piston of compressors (10) moves to form a first and second hydraulic variable volume of compressor (12, 134), and a blind liquid cylinder of expansion valves (30) in which a double-acting hydraulic piston of expansion valves (39) moves to form a first and second hydraulic variable volume of expansion valve (44, 46), said hydraulic variable volumes (12, 134, 44, 46) communicating with compressor and expansion valve gas and liquid reservoirs (14, 29, 50, 55) in which are housed compressor and expansion valve heat exchange and accumulation means (16, 59, 139, 70), this to form a compressor (3) and a regulator (4). Figure for the abbreviation: Fig. 4

Description

Title of the invention: Grouped mechanical-liquid piston heat pump

[0001] The present invention relates to a heat pump with grouped mechanical-liquid pistons, which is reversible, and whose main purpose is to air condition and heat residential, commercial, or industrial buildings.

[0002] In the context of the ecological transition, heat pumps occupy a strategic place because they can heat buildings at a lower energy cost by extracting renewable heat from the environment.

[0003] Building heating alone absorbs more than twenty percent of the world's primary energy, and that is why the market for low-temperature heat pumps, the most efficient, is set to grow strongly in the coming years, but also that of high-temperature heat pumps, better suited to the renovation of old buildings which remain the majority.

[0004] As global warming worsens and lifestyles change, air conditioning in buildings already consumes more than ten percent of the electricity produced in the world.

[0005] This share is destined to grow significantly both in proportion and in volume, to the point that the efficiency of reversible heat pumps represents a major energy and economic challenge.

[0006] The principle of heat pumps currently used in the world is based mainly on the change of state, from vapor to liquid or vice versa, of a refrigerant fluid whose saturated vapor pressure is adapted to the target heating or cooling temperature range, and to the pressures that the installations can withstand.

[0007] Refrigeration cycles with a change of state, or phase, have the advantage of a high density of heating or cooling power because they exploit the latent heat of evaporation or condensation of a refrigerant by modulating the pressure and temperature of said fluid so that it evaporates or condenses at the opportune time.

[0008] In the current state of the art and technology and taking into account the economic, technological, physical, and manufacturing constraints of heat pumps, refrigeration cycles with change of state remain by far the most efficient.

[0009] However, not all refrigeration cycles use the change of state of a specially formulated refrigerant fluid.

[0010] For example, the Brayton-Joule cycle, also called the Bell-Coleman cycle, is based on the isentropic compression and expansion of a gas without a change of state, with, after said compression, the transfer of heat by said gas to a colder environment at constant pressure and with, after said expansion, the removal of heat by said gas from a container to be cooled, also at constant pressure.

[0011] However, the practical efficiency of the Bell-Coleman cycle remains low, with in practice a coefficient of performance barely above one and often even below one, unlike heat pumps with phase change and refrigerant, whose coefficient of performance can reach five to one or even more, which means that for one unit of energy invested, up to five or more units of energy are recovered in the form of heat or cooling.

[0012] Due to its low practical energy efficiency, the Bell-Coleman cycle is in practice only used when compressed air is naturally available, which may be the case in airplanes and on board certain trains.

[0013] Unlike Bell-Coleman cycle heat pumps, due to their high efficiency, refrigerant and phase change heat pumps are widely used for heating or cooling buildings.

[0014] And yet, the efficiency of refrigerant-based heat pumps remains far below the ideal Carnot efficiency which, taking into account the temperature differences usually used to carry out measurements, would give a coefficient of performance greater than twenty, while the best heat pumps currently on the market deliver a coefficient of performance of around five.

[0015] But the ideal Carnot efficiency is only an indicator of the maximum theoretically achievable efficiency because it does not take into account the temperature differences necessary for heat exchange to take place, nor the mechanical, electromechanical and practical constraints of manufacturing heat pumps.

[0016] Obviously, there would be an important advantage, due to the scarcity of energy and the climatic and ecological issues related to said energy, in maximizing the efficiency coefficient of heat pumps used to produce heating, air conditioning or even refrigeration, as close as possible to the ideal Carnot efficiency.

[0017] Subject to having a high energy efficiency compression and expansion machine, it would indeed be possible to approach the efficiency of the ideal Carnot cycle by using a fluid remaining entirely in the gaseous state, that is to say without a change of state.

[0018] To achieve this objective, the compressor of said machine must compress a gas in two successive stages.

[0019] The first stage consists of an adiabatic compression which takes place until the temperature of said gas is high enough for it to release heat, for example, to a building heating circuit, while the second stage is an isothermal compression during which the temperature reached by said gas at the end of adiabatic compression is maintained during the rest of the compression of said gas, releasing the heat produced by said isothermal compression to said heating circuit as it is carried out, until said gas is discharged from said compressor.

[0020] Next, the regulator of said machine must expand the gas which has been previously compressed according to the reverse process to that which has just been described, also in two successive steps.

[0021] The first stage consists of an adiabatic expansion which occurs until the temperature of said gas is sufficiently low for it to absorb heat, for example, from the environment outside said building, while the second stage is an isothermal expansion during which the temperature reached by said gas at the end of the adiabatic expansion is maintained during the rest of the expansion of said gas, absorbing heat from said environment as needed to maintain said temperature during the rest of said isothermal expansion, and this until the gas is discharged from said expansion valve.

[0022] One of the advantages of such a heat pump is that it no longer requires the use of polluting, toxic or combustible refrigerants, some of which destroy the ozone layer or produce a powerful greenhouse effect.

[0023] No longer depending on refrigerants is of even greater importance as European regulations, as well as those of many countries, plan to ban refrigerants whose global warming potential is greater than or equal to one hundred and fifty times that of carbon dioxide from the year two thousand and thirty.

[0024] These regulatory provisions will reduce the number of refrigerants that can be used in conventional heat pumps, and will significantly impact the technology of said pumps, and may even increase the cost price of said pumps.

[0025] A possible substitute for the refrigerants currently used in conventional heat pumps is carbon dioxide, which is a non-polluting gas with a low specific global warming potential, but whose main disadvantage is high operating pressures of more than one hundred atmospheres, which makes the sealing and safety of the installations more difficult to guarantee.

[0026] Carbon dioxide also has the disadvantage of a relatively low efficiency when implemented in a conventional heat pump which cannot recover work from the expansion of the gas.

[0027] The other fluids considered are hydrocarbons, primarily propane, which remains a flammable gas, or ammonia, which is highly corrosive and toxic.

[0028] Due to its high toxicity, ammonia will remain permanently reserved for industrial or commercial installations, used for example to generate the cold needed for the refrigeration lines of department stores.

[0029] Hydrocarbon gases such as propane require that compression units be placed either outside buildings or in well-ventilated technical rooms to avoid any risk of gas accumulation which could ignite and cause an explosion.

[0030] Propane installations must also guarantee a total absence of gas leakage into the heat transfer fluid circuits that heat or cool the buildings, as such a leak could also cause an explosion.

[0031] We can therefore understand the great advantage of reproducing as faithfully as possible the ideal heat pump cycle of Sadi Carnot, by making a quasi-isothermal volumetric compressor and expansion valve which use a neutral, non-toxic and non-flammable fluid, which remains in a gaseous state during the entire cycle.

[0032] This method is only possible by imposing a stable setpoint temperature on the gas during its isothermal compression or expansion, which can be achieved with a medium that stores heat directly in a compression or expansion chamber, said medium being associated with means that export said heat during the compression phase, or that import said heat during the expansion phase.

[0033] Several concepts are based on single-phase compressors or expansion valves, close to isothermal, incorporating means of heat storage and import or export.

[0034] This is the case, for example, of the quasi-isothermal machine described in patent GB2534244, said machine comprising a piston which is oriented downwards and which has a structure for absorbing and releasing heat, said piston compressing a gas in a variable volume in the bottom of which resides a constant volume of fluid.

[0035] According to the invention of patent GB2534244, said piston compresses or expands said gas while forcing the latter to cool down or heat up in contact with the heat absorption and release structure, said structure being able to be made of metal sheets which, when out of the liquid, exchange heat with the gas, however, when they are immersed in said liquid, they exchange heat with the latter.

[0036] According to the invention of patent GB2534244, the liquid remains approximately immobile unlike liquid piston compressors in which the liquid is on the contrary mobile, which implies that said liquid should not be subjected to decelerations too great than that of terrestrial gravity under penalty of causing cavitation and panic of said liquid.

[0037] On the contrary, the invention of patent GB2534244 therefore makes it possible to manufacture a high-speed rotating compressor or expansion valve without driving the liquid in motion, which has the advantage of giving said compressor or expansion valve a high volumetric power density.

[0038] It is noted that the particular configuration of patent GB2534244 proposes a relatively classic connecting rod and crank system to actuate the piston carrying the heat absorption and restitution structure.

[0039] Another approach consists of moving a liquid by means of a piston which translates in a cylinder as provided for in patent CN111734604, said liquid, contrary to patent GB2534244, submerging a static heat sink.

[0040] Similar to patent CN111734604, many publications also report liquid pistons that alternately force a gas and a liquid through a porous medium or a heat accumulation and release system.

[0041] This technical approach is notably adopted by various research programs dedicated to energy storage systems in the form of compressed air, for example intended to accumulate renewable energy produced by offshore wind turbines.

[0042] It appears from most of these devices that the compression or expansion efficiency depends strongly on the total heat exchange surface between the gas, the liquid and the heat absorption and release structures of whatever nature, but also on the time allowed for said exchanges to take place.

[0043] To promote these exchanges, it is therefore preferable to produce compressors or expansion valves with slow rotation, this in return for a lower volumetric power.

[0044] Besides the time allowed for heat exchange to occur, the advantage of slow-rotating compressors or expanders is that they allow time for the transfer of gases to take place, so as to limit pressure losses at the inlet and outlet ports of said compressors and expanders.

[0045] Indeed, if these rotate slowly, their effective thermodynamic pressure-volume diagram will be close to the ideal theoretical diagram because it is less distorted by the transfer of gases, and the practical efficiency of a heat pump incorporating said compressors and expansion valves will be closer to the maximum theoretical efficiency achievable according to the ideal Carnot cycle.

[0046] Because indeed, the inertial forces which reduce the performance of the pilot valves and flaps responsible for transferring gases into or out of a compressor or an expansion valve evolve more or less with the square of the rotation speed of said compressor or said expansion valve.

[0047] This results in a delay in the opening and / or closing of said valves and flaps which impairs the efficiency of the thermodynamic cycle.

[0048] As a consequence of the above, a slow-rotating single-phase heat pump which compresses and expands a gas according to the Carnot cycle will a priori occupy more volume than its conventional equivalent in which the refrigerant passes successively from the gaseous state to the liquid state and vice versa, and in which the compressor operates at high speed.

[0049] The problem with slow-rotating compressors and expansion valves is that, at the same power, the mechanical parts that make them up are subjected to higher stresses than those that make up their faster equivalent, and that the large dimensions of said parts resulting from said stresses generate high energy losses by friction.

[0050] Besides the large size of said parts, the disadvantage of the slow rotation of said compressors or expanders is that it is unfavorable to the establishment of a hydrodynamic lubrication regime between said parts, whether for example at the friction interface of a piston in a cylinder, or at the pivot joints between said piston and a connecting rod, between said connecting rod and the crank of a crankshaft, and between the latter and a crankcase.

[0051] It would therefore be very advantageous to implement liquid pistons coupled with means of heat exchange, storage, restitution, import and export, by means of slow machines with high mechanical efficiency which leave a sufficiently long time on the one hand, for heat exchanges to maximize their efficiency, and on the other hand, for the transfer of gases to minimize energy losses.

[0052] Such a configuration would make it possible to produce high energy performance heat pumps, delivering an efficiency closer to that of the ideal Carnot cycle than their conventional counterparts which operate a refrigerant with a change of state, and requiring for example only atmospheric air and water to operate, or nitrogen which is non-reactive by nature and non-polluting associated with a low melting point liquid such as ethanol, a harmless, non-toxic product, and commonly used in indoor stoves without chimney flues.

[0053] It would, for example, be possible to obtain from said configuration a coefficient of performance of the order of six or seven, whereas under the same measurement conditions and in In the same environment, the coefficient of performance of the best refrigerant-based heat pump on the market would be around five.

[0054] But, as previously described, to obtain such a performance gap, it is necessary to carry out almost isothermal compression and expansion by promoting heat exchanges as much as possible during said compression and said expansion, limiting losses by transfer, losses by internal or external gas leaks as much as possible, and limiting losses by friction as much as possible.

[0055] For example, the coefficient of performance of a single-phase Carnot cycle heat pump, given its need to compress a larger quantity of gas than its counterpart with a refrigerant in a change of state, is necessarily very sensitive to the energy efficiency of its mechanical transmission device, said efficiency, if insufficient, resulting in said single-phase Carnot cycle heat pump having a lower efficiency than its said counterpart.

[0056] Indeed, since a single-phase Carnot cycle heat pump has to compress a larger quantity of gas than its phase-change refrigerant counterpart, the coefficient of performance of said single-phase heat pump is very dependent on the energy efficiency of its mechanical transmission device for gas compression and expansion.

[0057] If said efficiency is insufficient, said single-phase heat pump will have a lower coefficient of performance than its refrigerant-based counterpart.

[0058] This sensitivity to the mechanical efficiency of compression and expansion of a single-phase Carnot cycle heat pump is all the greater when, for example, a coefficient of performance greater than five is targeted.

[0059] For example, a single-phase Carnot cycle heat pump which delivers ten kilowatts of thermal power with a coefficient of performance of five, requires an external energy input of two kilowatts in the form of mechanical work.

[0060] If the mechanical efficiency of said single-phase heat pump is poor and results in a mechanical loss of one kilowatt, the coefficient of performance of said pump drops from five to three point three, and the energy bill of the owner of said pump increases by fifty percent.

[0061] In this case, the single-phase heat pump loses all or almost all of its interest compared to its conventional equivalent with a refrigerant that changes state.

[0062] This is why the heat pump with grouped mechanical-liquid pistons according to the invention features an innovative configuration with very high mechanical and volumetric efficiency, coupled with efficient heat exchanges and fluxes, so as to provide, in particular to single-phase Carnot cycle heat pumps which result in a significantly higher coefficient of performance than that of their conventional equivalent with phase-change refrigerant.

[0063] Thus, the heat pump with grouped mechanical-liquid pistons according to the invention is mainly intended to produce heat pumps with a high coefficient of performance, particularly in the field of high temperatures, where conventional phase-change heat pumps are notoriously inefficient.

[0064] This constitutes a decisive advantage because producing pumps delivering high efficiency at high temperatures makes it possible to reuse most existing heating installations and to drastically reduce the cost of installing said pumps compared to their conventional counterparts without prejudice to the energy bill.

[0065] These advantages strongly promote the adoption of heat pumps by households, who are often put off by the cost of installation.

[0066] In France, for example, more than eighty percent of French homes were built before the year 2000 and are most often equipped with old heating systems.

[0067] Still in France, detached houses make up more than fifty-six percent of main residences, three-quarters of which meet energy classes C, D and E and therefore require a significant amount of heat to ensure an acceptable level of comfort for their occupants.

[0068] A high-efficiency, high-temperature heat pump park also makes it possible to reduce the national electricity power requirement during periods of extreme cold.

[0069] In France, for example, record power due to cold weather has exceeded one hundred gigawatts, while the electrification of uses and the promotion of heat pumps promoted by public authorities will make heating even more dependent on electricity production.

[0070] However, the efficiency of air-to-water heat pumps, which are most likely to develop, is lower the lower the outside temperature and the higher the heating power to be delivered to the heating radiators, which implies delivering high-temperature water to said radiators.

[0071] Moreover, periods of extreme cold are often associated with a lack of wind and sun, which excludes any significant contribution from new renewable wind and solar energies to deliver the electrical power needed to heat homes.

[0072] In this context, reducing the electricity consumption of the French national fleet of heat pumps by only twenty percent will be equivalent in the future to avoiding the construction of several nuclear reactors which in ordinary times would be underutilized.

[0073] For at least all these reasons, it results in particular from the heat pump with grouped mechanical-liquid pistons according to the invention a heat pump: • Which can easily be installed in place of a gas or oil boiler, operating in the same temperature ranges, and reusing pre-existing heat emitters, for example high-temperature radiators; • Which, depending on the external and internal temperature conditions of the buildings, delivers a higher coefficient of performance than that of conventional heat pumps with refrigerant in phase change, said pump according to the invention thus reducing, all other things being equal, the energy required for the production of heat or cold; • Whose thermodynamic efficiency is close to that of the ideal Carnot cycle which is by definition unsurpassable, to the point that in all likelihood, the replacement of said heat pump by another concept can hardly be motivated by a further improvement in efficiency; • Which may not use any flammable, corrosive, or harmful refrigerant, the said pump being able to operate, for example, with atmospheric air or nitrogen and evade any regulatory or safety constraints relating to the handling, storage or recycling of refrigerants; • Whose operating temperature range is very wide due to the fact that said pump is not dependent on any refrigerant whatsoever, said pump being able to operate in heating or air conditioning mode in any region of the world without prejudice to its efficiency; • Of simple design, to the point that said pump can be produced in virtually every country in the world in workshops with a modest technical level, in particular by assembling low-cost components that are easily manufactured or widely available on the market; • Whose simple mechanical configuration allows for maintenance without great technical skill, and at a lower cost; • Which allows any qualified plumber-heating engineer to easily and affordably install a heating and air conditioning network that integrates seamlessly into buildings and their surrounding environment, this without requiring any approval or certification related to the handling of gases that are hazardous to health and the environment; • Whose robust mechanism gives it a lifespan which can reach, subject to the replacement of minor parts, several decades without deterioration of either the operation or the performance of said pump, such a lifespan constituting an additional advantage of said pump for the environment compared with conventional heat pumps with refrigerant fluid when analyzing the entire life cycle of said pumps, including manufacturing and recycling; • Which is silent and can be integrated into buildings while producing minimal noise; • Whose external heat sensors can easily be extra-flat and large surface area, thus reducing or even eliminating the electrical consumption of ventilation and noise pollution from the neighborhood; • Whose arrangement allows large heat exchange surfaces to be exposed to the environment at a lower cost, by using low-speed, low-energy-consumption, low-noise motor fans; • Whose manufacture requires neither rare or strategic materials, nor high-tech know-how and knowledge; • Whose recyclability rate is high, being made up of massive parts that are easy to isolate and reintegrate into the production of new parts.

[0074] It is understood that the heat pump with grouped mechanical-liquid pistons according to the invention is intended, in addition to heat pumps, for any other application similar in its concept and principle which could advantageously take advantage of the particular characteristics and functionalities of said mechanical-liquid piston heat pump according to the invention.

[0075] The other features of the present invention have been described in the description and in the secondary claims directly or indirectly dependent on the main claim.

[0076] The mechanical-liquid piston heat pump according to the present invention comprises at least one compressor in which at least one pneumatic variable compressor volume is formed, and at least one expansion valve in which at least one pneumatic variable expansion valve volume is formed, each said volume having, on the one hand, an inlet port through which a working gas can enter and, on the other hand, an outlet port through which said gas can exit, said pump comprising: At least one blind liquid cylinder of compressors which is directly or indirectly attached to a static frame, each end of which is sealed by a sealed compressor cylinder termination, and in which at least one double-acting hydraulic piston of compressors can translate in a sealed manner, which has, on the one hand, at least one first axial face of compressor piston which forms with said cylinder and one of the sealed compressor cylinder terminations a first hydraulic variable volume of compressor, and on the other hand, at least one second axial face of compressor piston which forms with said cylinder and the other sealed compressor cylinder termination a second hydraulic variable volume of compressor, the two said hydraulic variable volumes being wholly or partly filled with a working liquid; At least one first compressor gas and liquid reservoir which is connected to the first hydraulic variable volume of the compressor by a communication conduit, such that said reservoir fills mostly or totally with working liquid when the first hydraulic variable volume of the compressor is minimal, said reservoir fills partially or totally with working gas when the first hydraulic variable volume of the compressor is maximal, the variation in the volume of the working gas contained in the first compressor gas and liquid reservoir defining, on the one hand, a pneumatic variable volume of the compressor and being, on the other hand, approximately equal to the variation in the volume of the working liquid contained in the first hydraulic variable volume of the compressor; At least one second compressor gas and liquid reservoir which is connected to the second hydraulic variable volume of the compressor by a communication conduit, such that said reservoir fills mostly or totally with working liquid when the second hydraulic variable volume of the compressor is minimal, said reservoir fills partially or totally with working gas when the second hydraulic variable volume of the compressor is maximal, the variation in the volume of the working gas contained in the second compressor gas and liquid reservoir defining, on the one hand, a pneumatic variable volume of the compressor and being, on the other hand, approximately equal to the variation in the volume of the working liquid contained in the second hydraulic variable volume of the compressor; At least one blind liquid cylinder of expansion valves which is directly or indirectly attached to the static frame, the ends of which are sealed by a sealed termination of the regulator cylinder, and in which at least one double-acting hydraulic regulator piston can translate in a sealed manner, said piston having, on the one hand, at least one first axial face of the regulator piston which forms with said cylinder and one of the sealed terminations of the regulator cylinder a first hydraulic variable regulator volume, and on the other hand, at least one second axial face of the regulator piston which forms with said cylinder and the other sealed termination of the regulator cylinder a second hydraulic variable regulator volume, the two said hydraulic variable volumes being wholly or partly filled with a working fluid; At least one first expansion valve gas and liquid reservoir which is connected to the first hydraulic expansion valve variable volume by a communication conduit, such that said reservoir fills mostly or totally with working liquid when said first hydraulic expansion valve variable volume is minimal, said reservoir fills partially or totally with working gas when said first hydraulic compressor variable volume is maximal, the variation in the volume of the working gas contained in the first expansion valve gas and liquid reservoir defining, on the one hand, a pneumatic expansion valve variable volume and being, on the other hand, approximately equal to the variation in the volume of the working liquid contained in the first hydraulic expansion valve variable volume; At least one second regulator gas and liquid reservoir which is connected to the second hydraulic regulator variable volume by a communicating conduit, such that said reservoir fills mostly or totally with working liquid when the second hydraulic regulator variable volume is minimal, said reservoir fills partially or totally with working gas when said second hydraulic regulator variable volume is maximal, the variation in the volume of the working gas contained in the second regulator gas and liquid reservoir defining, on the one hand, a pneumatic regulator variable volume and being, on the other hand, approximately equal to the variation in the volume of the working liquid contained in the second hydraulic regulator variable volume; First compressor heat exchange and accumulation means housed in the first compressor gas and liquid reservoir, and second compressor heat exchange and accumulation means housed in the second compressor gas and liquid reservoir, said means being able to primarily take heat from the working gas contained in the reservoir in which they are housed, and temporarily store said heat, before transferring it to the working fluid also contained in said reservoirs; First means of heat exchange and accumulation of the regulator which are housed in the first regulator gas and liquid tank and second means of heat exchange and accumulation of the regulator which are housed in the second regulator gas and liquid tank, said means being able to principally take heat from the working liquid which is contained in the tank in which they are housed, and temporarily store said heat, before transferring it to the working gas which is also contained in said tanks; First means of heat export located inside and / or outside the first compressor gas and liquid tank and second means of heat export located inside and / or outside the second compressor gas and liquid tank, said means, taking heat directly or indirectly respectively from the first means of compressor heat exchange and accumulation and from the second means of compressor heat exchange and accumulation on the one hand, and / or from the working liquid and / or working gas contained in whole or in part in said tanks, on the other hand, said heat being subsequently transferred to heating means external to said tanks; First means of heat import located inside and / or outside the first gas and liquid expansion tank and second means of heat import located inside and / or outside the second gas and liquid expansion tank, said means, directly or indirectly supplying heat respectively to the first means of heat exchange and accumulation of expansion tank and to the second means of heat exchange and accumulation of expansion tank on the one hand, and / or to the working liquid and / or working gas contained in whole or in part in said tanks, on the other hand, said heat having been previously taken from cooling means external to said tanks; Compressor filling means that permit or prohibit the passage of working gas from a compressor inlet plenum to the first compressor gas and liquid reservoir via at least one inlet port, while other compressor filling means permit or prohibit the passage of working gas from said plenum or from another compressor inlet plenum to the second compressor gas and liquid reservoir via at least one other inlet port; Compressor draining means that permit or prohibit the passage of working gas from the first compressor gas and liquid tank to a compressor discharge plenum via at least one outlet port, while other compressor draining means permit or prohibit the passage of working gas from the second compressor gas and liquid tank to said plenum or to another compressor discharge plenum via at least one other outlet port; Regulator filling means that permit or prohibit the passage of working gas from a regulator inlet plenum to the first regulator gas and liquid reservoir via at least one inlet port, while other regulator filling means permit or prohibit the passage of working gas from said plenum or from another regulator inlet plenum to the second regulator gas and liquid reservoir via at least one other inlet port; Regulator draining means that permit or prohibit the passage of working gas from the first regulator gas and liquid reservoir to a regulator discharge plenum via at least one outlet port, while other regulator draining means permit or prohibit the passage of working gas from the second regulator gas and liquid reservoir to said plenum or to another regulator discharge plenum via at least one other outlet port; A compressor connecting rod which is integral with the double-acting hydraulic piston of compressors, which passes in a sealed manner through at least one of the sealed terminations of the compressor cylinder and which is approximately parallel to the longitudinal axis of said piston and of the blind liquid cylinder of compressors; A connecting rod of regulators which is integral with the double-acting hydraulic piston of regulators, which passes in a sealed manner through at least one of the sealed terminations of the regulator cylinder, and which is approximately parallel to the longitudinal axis of said piston and of the blind liquid cylinder of regulators; Compressor piston guiding means which keep the double-acting hydraulic compressor piston and compressor connecting rod parallel to the blind liquid cylinder of the compressor, regardless of the position of said piston in said cylinder; Piston guide means for pressure regulators that support the double-acting hydraulic piston of pressure regulators and the connecting rod of pressure regulators parallel to the blind liquid cylinder of expansion valves, regardless of the position of said piston in said cylinder; • Means of actuating connecting rods through which at least one drive motor imparts, on the one hand, to the connecting rod of compressors a reciprocating longitudinal translational movement parallel to the axis of the blind liquid cylinder of compressors, and on the other hand, to the connecting rod of expansion valves a reciprocating longitudinal translational movement parallel to the axis of the blind liquid cylinder of expansion valves; • Means of storing mechanical energy which are directly or indirectly connected to the means of actuating connecting rods or which are directly or indirectly connected to the connecting rod of expansion valves or to the connecting rod of compressors, said means of storage being able to alternately take and give mechanical energy to said actuating means or to said rods.

[0077] The mechanical-liquid piston heat pump according to the present invention comprises connecting rod actuating means which consist of a crankshaft which can rotate in at least one shaft bearing which is directly or indirectly attached to the static frame, said crankshaft having at least one crank around which is articulated a connecting rod head of an actuating connecting rod, the latter also having a connecting rod foot which is articulated as appropriate either with the connecting rod of compressors, or with the connecting rod of expansion valves.

[0078] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises a crankshaft which has two cranks, the first of said cranks being connected by a first actuating rod to the connecting rod of compressors while the second of said cranks is connected by a second actuating rod to the connecting rod of expansion valves.

[0079] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises a connecting rod foot which articulates, as appropriate, with the connecting rod of compressors or with the connecting rod of expansion valves by means of a connecting bracket which is integral with said rod.

[0080] The mechanical-liquid piston heat pump according to the present invention comprises a connecting arm which includes an arm yoke which is traversed by an arm axis which is perpendicular, as the case may be, to the connecting rod of compressors or to the connecting rod of expansion valves, and around which are articulated on the one hand, a connecting rod foot bearing which includes the connecting rod foot, and at least one arm roller which rolls on at least one arm bearing track which is parallel, as the case may be, to the blind liquid cylinder of compressors or to the blind liquid cylinder of expansion valves, and which is directly or indirectly integral with said cylinder.

[0081] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises first means for exchanging and storing compressor heat and / or second means for exchanging and storing compressor heat and / or first means for exchanging and storing expansion valve heat and / or second means for exchanging and storing expansion valve heat which are made of a porous medium which has porosities into which working liquid and working gas alternately enter and exit.

[0082] The pump with grouped mechanical-liquid pistons according to the present invention comprises first heat export means consisting of a circulating portion of the working fluid exiting the first hydraulic variable volume of the compressor and / or the first gas and liquid reservoir of the compressor via a liquid outlet duct, said circulating portion then returning to said first volume and / or to said first reservoir via a liquid inlet duct, this after having directly or indirectly transferred heat to the heating means

[0083] The grouped mechanical-liquid piston heat pump according to the present invention includes second heat export means which consist of a circulating portion of the working liquid which exits the second hydraulic variable volume of the compressor and / or the second gas and liquid tank of the compressor via a liquid outlet duct, said circulating portion then returning to said second volume and / or to said second tank via a liquid inlet duct, this after having directly or indirectly transferred heat to the heating means.

[0084] The grouped mechanical-liquid piston heat pump according to the present invention comprises a circulating portion of the working fluid which transfers heat to the heating means via at least one secondary heating heat exchanger.

[0085] The grouped mechanical-liquid piston heat pump according to the present invention includes first heat import means which consist of a circulating part of the working liquid which exits the first hydraulic variable volume of the expansion valve and / or the first gas and liquid expansion valve reservoir via a liquid outlet conduit to return to said first volume and / or to said first reservoir via a liquid inlet conduit, this after having directly or indirectly taken heat from the cooling means.

[0086] The mechanical-liquid piston heat pump according to the present invention comprises secondary heat import means consisting of a circulating portion of the working fluid exiting the second hydraulic variable volume of the expansion valve and / or the second gas and liquid expansion valve reservoir via a liquid outlet conduit to return to said second volume and / or to said second reservoir via a liquid inlet conduit, this after having directly or indirectly absorbed heat from the cooling means.

[0087] The grouped mechanical-liquid piston heat pump according to the present invention comprises a circulating portion of the working fluid which takes heat from the cooling means through at least one secondary cooling heat exchanger.

[0088] The grouped mechanical-liquid piston heat pump according to the present invention includes first heat export means which consist of at least one heat exchanger duct housed in the first compressor gas and liquid tank and in which circulates a heat transfer fluid which exports heat taken from the first compressor heat exchange and accumulation means on the one hand, and / or from the working liquid and / or from the working gas contained in the first compressor gas and liquid tank on the other hand, to the heating means, via heat transport ducts.

[0089] The grouped mechanical-liquid piston heat pump according to the present invention includes second heat export means which consist of at least one heat exchanger duct housed in the second compressor gas and liquid tank and in which circulates a heat transfer fluid which exports heat taken from the second compressor heat exchange and accumulation means on the one hand, and / or from the working liquid and / or from the working gas contained in the second compressor gas and liquid tank on the other hand, to the heating means, via heat transport ducts.

[0090] The grouped mechanical-liquid piston heat pump according to the present invention includes first heat import means which consist of at least one heat exchanger duct housed in the first expansion valve gas and liquid tank and in which circulates a heat transfer fluid which imports heat from the cooling means to the first expansion valve heat exchange and accumulation means on the one hand, and / or the working liquid and / or the working gas contained in the first expansion valve gas and liquid tank on the other hand, via heat transport ducts.

[0091] The mechanical-liquid piston heat pump according to the present invention comprises secondary heat import means consisting of at least one heat exchanger conduit housed in the second expansion valve gas and liquid reservoir and through which circulates a heat transfer fluid that imports heat from the cooling means to the secondary expansion valve heat exchange and accumulation means on the one hand, and / or the working fluid and / or the working gas contained in the second gas tank and regulator liquid on the other hand, via heat transport ducts.

[0092] The grouped mechanical-liquid piston heat pump according to the present invention comprises first means for exchanging and storing compressor heat and / or second means for exchanging and storing compressor heat which consist of at least one liquid spray nozzle supplied by a liquid spray pump, said nozzle being able, as appropriate, to atomize working liquid into fine droplets in the internal volume of the first compressor gas and liquid reservoir or in the internal volume of the second compressor gas and liquid reservoir.

[0093] The grouped mechanical-liquid piston heat pump according to the present invention comprises first means for heat exchange and accumulation of expansion valve and / or second means for heat exchange and accumulation of expansion valve which consist of at least one liquid spray nozzle supplied by a liquid spray pump, said nozzle being able, as appropriate, to atomize working liquid into fine droplets in the internal volume of the first expansion valve gas and liquid reservoir or in the internal volume of the second expansion valve gas and liquid reservoir.

[0094] The grouped mechanical-liquid piston heat pump according to the present invention comprises first compressor heat exchange and accumulation means and / or second compressor heat exchange and accumulation means which consist of a rotary liquid atomizer which includes a rotating atomizing cylinder pierced with radial atomizing orifices, an atomizer motor driving said cylinder in rotation sufficiently rapid so that the latter draws working liquid into its axial end by centrifugal effect and / or by means of a pumping turbine, and radially discharges said liquid in the form of fine droplets into the internal volume of the first compressor gas and liquid reservoir if said atomizer is housed in said first reservoir, or into the internal volume of the second compressor gas and liquid reservoir if said atomizer is housed in said second reservoir, via the radial atomizing orifices..

[0095] The pump with grouped mechanical-liquid pistons according to the present invention comprises first means for heat exchange and accumulation of expansion valve heat and / or second means for heat exchange and accumulation of expansion valve heat, which consist of a rotary liquid atomizer comprising a rotating atomizing cylinder perforated with radial atomizing orifices, an atomizer motor driving said cylinder in rotation sufficiently rapid so that the latter draws working liquid into its axial end by centrifugal force and / or by means of a pumping turbine, and radially discharges said liquid in the form of fine droplets into the internal volume of the first gas and liquid regulator reservoir if said atomizer is housed in said first reservoir, or in the internal volume of the second gas and liquid regulator reservoir if said atomizer is housed in said second reservoir, via the radial atomization ports.

[0096] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises compressor piston guiding means and / or expansion piston guiding means which consist of at least one sliding pivot joint formed on the one hand, between an external cylindrical surface presented by the compressor connecting rod and the expansion connecting rod, and on the other hand, a guide orifice provided in the sealed termination(s) of the compressor cylinder through which the compressor connecting rod passes in the case of the latter, or a guide orifice provided in the sealed termination(s) of the expansion cylinder through which the expansion connecting rod passes in the case of said expansion connecting rod.

[0097] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises a sliding pivot joint which includes an articulated connecting tube which has at one of its ends a sealed ball joint of rod which articulates as appropriate around the connecting rod of compressors or around the connecting rod of expansion valves, said articulated tube having at its other end a sealed ball joint of termination which articulates as appropriate with the sealed termination of compressor cylinder or with the corresponding sealed termination of expansion cylinder.

[0098] The heat pump with grouped mechanical-liquid pistons according to the present invention includes piston guiding means for compressors and / or piston guiding means for expansion valves which consist of a guide skirt arranged on the periphery of the double-acting hydraulic piston of compressors or on the periphery of the double-acting hydraulic piston of expansion valves, said skirt being able to translate with little clearance in the blind liquid cylinder of compressors or in the corresponding blind liquid cylinder of expansion valves.

[0099] The heat pump with grouped mechanical-liquid pistons according to the present invention includes compressor filling means and / or compressor draining means which consist of at least one compressor valve and / or at least one piloted compressor valve.

[0100] The heat pump with grouped mechanical-liquid pistons according to the present invention includes means for filling the expansion valve and / or means for emptying the expansion valve which consist of at least one piloted expansion valve.

[0101] The group mechanical-liquid piston heat pump according to the present invention comprises a compressor discharge plenum which is connected to the plenum expansion valve inlet via a high-pressure gas line such that the working gas exiting the pneumatic variable volumes of the compressor via said compressor discharge plenum is introduced into the pneumatic variable volumes of the expansion valve via said expansion valve inlet plenum, while the expansion valve discharge plenum is connected to the compressor inlet plenum by a low-pressure gas line such that the working gas exiting the pneumatic variable volumes of the expansion valve via said expansion valve discharge plenum is introduced into the pneumatic variable volumes of the compressor via said compressor inlet plenum.

[0102] The heat pump with grouped mechanical-liquid pistons according to the present invention includes a high-pressure gas conduit which communicates with at least one high-pressure gas reservoir.

[0103] The heat pump with grouped mechanical-liquid pistons according to the present invention includes a low-pressure gas conduit which communicates with at least one low-pressure gas reservoir.

[0104] The group mechanical-liquid piston heat pump according to the present invention comprises a working gas which flows in the high-pressure gas duct which transfers its heat to the working gas which flows in the low-pressure gas duct via a regeneration heat exchanger.

[0105] The grouped mechanical-liquid piston heat pump according to the present invention comprises a compressor inlet plenum and a compressor outlet plenum which are part of a compressor cylinder head which covers the upper part of the first compressor gas and liquid tank and the second compressor gas and liquid tank, the latter being themselves positioned mainly above the blind liquid cylinder of compressors, so that, under the effect of Earth's gravity, the working gas is always first to exit said tanks, via said outlet plenum while the working liquid is always first to enter said tanks, via said inlet plenum.

[0106] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises an expansion valve inlet plenum and an expansion valve outlet plenum which are part of an expansion valve cylinder head which covers the upper part of the first expansion valve gas and liquid reservoir and the second expansion valve gas and liquid reservoir, the latter being themselves positioned mainly above the blind expansion valve liquid cylinder, so that, under the effect of Earth's gravity, the working gas is always first to exit said reservoirs, via said outlet plenum, while the working liquid is always first to enter said reservoirs, via said inlet plenum.

[0107] The heat pump with grouped mechanical-liquid pistons according to the present invention includes mechanical energy storage means which consist of a flywheel made rotationally fixed to the crankshaft by a transmission multiplier.

[0108] The grouped mechanical-liquid piston heat pump according to the present invention comprises a crankshaft which includes a toothed ring which the drive motor drives in rotation by means of at least one ring drive pinion whose pitch diameter is smaller than that of said ring, the latter and said pinion forming a multiplication gear system.

[0109] The heat pump with grouped mechanical-liquid pistons according to the present invention comprises outlet ports which open into the compressor discharge plenum or those which open into the expansion valve discharge plenum, each of which forms an overflow tank in which working fluid can be stored, said tank being arranged so that when the compressor draining means or, as the case may be, the expansion valve draining means, allow the passage of working gas via said ports, said gas must pass through said tank before opening, as the case may be, into the compressor discharge plenum or into the expansion valve discharge plenum.

[0110] The heat pump with grouped mechanical-liquid pistons according to the present invention includes overflow tanks formed by the outlet ports of the first compressor gas and liquid tank and those of the second compressor gas and liquid tank which open into the same compressor discharge plenum but which are separated by a leveling dike which tends to equalize the working liquid levels in said tanks when the compressor draining means associated with said tanks prevent the passage of working gas.

[0111] The heat pump with grouped mechanical-liquid pistons according to the present invention includes overflow tanks formed by the outlet ports of the first gas and liquid expansion tank and those of the second gas and liquid expansion tank which open into the same expansion discharge plenum but which are separated by a leveling dike which tends to equalize the working liquid levels in said tanks when the expansion draining means associated with said tanks prevent the passage of working gas.

[0112] The heat pump with grouped mechanical-liquid pistons according to the present invention includes a working liquid level equalization valve which can connect the first compressor gas and liquid tank or the second compressor gas and liquid tank with the first expansion valve gas and liquid tank or the second expansion valve gas and liquid tank.

[0113] The grouped mechanical-liquid piston heat pump according to the present invention includes a defrosting heat reservoir which is heated by the first heat export means and / or the second heat export means and which can transfer its heat to the cooling means.

[0114] The grouped mechanical-liquid piston heat pump according to the present invention includes a defrosting heat reservoir which is formed of a heat transfer fluid reservoir connected in bypass of the heat transport duct which carries the heat transfer fluid to the cooling means, said fluid being able either to pass through said reservoir before reaching the cooling means to heat the latter, or to bypass said reservoir to reach said means directly.

[0115] The following description, with reference to the attached drawings given by way of non-limiting examples, will allow for a better understanding of the invention, its features, and the advantages it is likely to provide:

[0116] [Fig-1] is a pressure-volume diagram of the thermodynamic cycle executed by the grouped mechanical-liquid piston heat pump according to the invention when said pump is not equipped with a regeneration heat exchanger.

[0117] [Fig.2] is a pressure-volume diagram of the thermodynamic cycle executed by the grouped mechanical-liquid piston heat pump according to the invention when said pump is equipped with a regeneration heat exchanger.

[0118] [Fig.3] is a schematic cross-sectional view of the grouped mechanical-liquid piston heat pump according to the invention, in which the blind liquid cylinder of compressors and the blind liquid cylinder of expansion valves are aligned essentially for simplicity of representation, the means of heat exchange and accumulation of compressor and expansion valve being made of a porous medium, while the first and second means of heat export are formed of a circulating part of the working liquid which exchanges heat with the heating means via a secondary heating heat exchanger, while the first and second means of heat import are formed of a circulating part of the working liquid which exchanges heat with the cooling means via a secondary cooling heat exchanger.

[0119] [Fig.4] is a schematic cross-sectional view of the grouped mechanical-liquid piston heat pump according to the invention and according to the architecture shown in [Fig.3], the means for heat exchange and accumulation of the compressor and expansion valve being made up of liquid spray nozzles supplied by liquid spray pumps, while the means for exporting heat to the heating means and importing heat from the cooling means are formed by heat exchanger ducts in which a heat transfer fluid circulates, while a partitioned thermal-insulated enclosure separates the compressors, on the one hand, expansion valves, and on the other hand, means for actuation of connecting rods, the drive motor and means for storing mechanical energy, said enclosure also thermally separating said heat pump from the external environment.

[0120] [Fig.5] is a schematic cross-sectional view of the grouped mechanical-liquid piston heat pump according to the invention, still according to the architecture shown in [Fig.3], the compressor and expansion heat exchange and accumulation means being made up of rotating liquid atomizers, while the first and second heat export means are formed of a circulating part of the working liquid which exchanges heat with the heating means via a secondary heating heat exchanger, while the first and second heat import means are formed of a circulating part of the working liquid which exchanges heat with the cooling means via a secondary cooling heat exchanger.

[0121] [Fig.6] is a three-dimensional view of the grouped mechanical-liquid piston heat pump according to the invention, in which the blind liquid cylinders of compressors and expanders are juxtaposed and parallel, while the connecting rods of compressors and expanders are simultaneously set in motion by the same drive motor and the same flywheel via a common crankshaft equipped with two cranks, the transmission casing housing in particular the transmission multiplier and the multiplication gear system and being cut to show its contents, however, the means for exchanging and storing heat of compressor and expander are made up of rotating liquid atomizers and the means for exporting and importing heat are formed of heat exchanger ducts in which a heat transfer fluid circulates.

[0122] [Fig.7] is a three-dimensional view of the mechanical piston heat pump liquids shown in [Fig.6], from another point of view.

[0123] [Fig.8] is a longitudinal sectional side view of the grouped mechanical-liquid piston heat pump according to the invention shown in [Fig.6], said section passing through the center of the first and second compressor gas and liquid tanks.

[0124] [Fig.9] is a cross-sectional view of the mechanical piston heat pump liquids grouped according to the invention shown in [Fig.6], said section passing through the center of the first compressor gas and liquid tank and the first expansion valve gas and liquid tank.

[0125] [Fig. 10] is a longitudinal sectional view from below of the grouped mechanical-liquid piston heat pump according to the invention shown in [Fig.6], said section passing through the center of the blind liquid cylinders of compressors and expansion valves.

[0126] [Fig. 11] is a three-dimensional cross-sectional view of the grouped liquid-mechanical piston heat pump according to the invention shown in [Fig. 6], which shows in in particular the articulated actuation rod with the connecting rods of compressors and expansion valves via a connecting hook.

[0127] [Fig. 12] is an exploded three-dimensional view of the double-acting hydraulic compressor piston fixed to its compressor connecting rod, the connecting rod with which said piston cooperates, the connecting cross, the cross rollers and the cross bearing track which also cooperate with said piston, all these components forming part of the mechanical-liquid piston heat pump grouped according to the invention as shown in [Fig. 6].

[0128] [Fig. 13] is a schematic cross-sectional view of the compressor cylinder head which covers the first and second compressor gas and liquid tanks of the grouped mechanical-liquid piston heat pump according to the invention, said view showing the expulsion of excess working liquid to the overflow tank of the first said gas and liquid tank when the first hydraulic variable volume of the compressor reaches its minimum volume, together with the expulsion of working gas to the compressor discharge plenum in which said tank is arranged.

[0129] [Fig. 14] is the same view of the grouped mechanical-liquid piston heat pump according to the invention as that shown in [Fig. 13], except that it illustrates the reintroduction into the first compressor gas and liquid tank of all or part of the working liquid previously expelled to the overflow tank arranged in the compressor discharge plenum, said reintroduction occurring after the first hydraulic variable volume of the compressor has passed through its minimum volume and while said hydraulic variable is enlarging again and the piloted compressor valve which forms the compressor draining means of the first compressor gas and liquid tank remains provisionally ajar.

[0130] [Fig. 15] is the same view of the grouped mechanical-liquid piston heat pump according to the invention as that shown in [Fig. 14], except that it illustrates what occurs after the compressor pilot valve which forms the compressor draining means of the first compressor gas and liquid reservoir has closed after sufficient working liquid has been reintroduced from the overflow tank into said first reservoir, and the compressor pilot valve which forms the compressor filling means of said first reservoir has opened to admit working gas from the compressor inlet plenum.

[0131] DESCRIPTION OF THE INVENTION:

[0132] Figures 1 to 15 show the grouped mechanical-liquid piston heat pump 1 according to the invention, various details of its components, its variants, and its accessories.

[0133] As can be seen in Figures 3 to 7, 9 to 11 and 13 to 15, the grouped mechanical-liquid piston heat pump 1 according to the invention comprises at least one compressor 3 in which is formed at least one pneumatic variable volume of compressor 2, and at least one expansion valve 4 in which is formed at least one pneumatic variable volume of expansion valve 136, each said volume 2, 136 comprising on the one hand, an inlet port 6 through which a working gas 5 can enter and on the other hand, an outlet port 7 through which said gas 5 can exit.

[0134] It has been shown in Figures 3 to 7 and 9 to 11 that the grouped mechanical-liquid piston heat pump 1 according to the invention also comprises at least one blind liquid cylinder of compressors 8 which is directly or indirectly integral with a static frame 40, each end of which is sealed by a sealed termination of a compressor cylinder 135, and in which at least one double-acting hydraulic piston of compressors 10 can translate in a sealed manner, which has, on the one hand, at least one first axial face of a compressor piston 132 which forms with said cylinder 8 and one of the sealed terminations of a compressor cylinder 135 a first hydraulic variable volume of a compressor 12, and on the other hand, at least one second axial face of a compressor piston 133 which forms with said cylinder 8 and the other sealed termination of a compressor cylinder 135 a second hydraulic variable volume of a compressor 134, the two said hydraulic variable volumes 12,134 being wholly or partly filled with a working fluid 13. ,

[0135] It is noted that the double-acting hydraulic piston of compressors 10 and the double-acting hydraulic piston of expansion valves 39 can be made up of one or more coaxial cylindrical sections and one or more coaxial sealed discs, and include at least one sealing gasket 51, whether the latter is toroidal, lip, composite, or of a type known to those skilled in the art, said gasket 51 preventing the working fluid 13 from leaking between said pistons 10, 39 and their respective blind fluid cylinder 8, 30.

[0136] As an alternative to said sealing joint 51, at least one segment with cut or continuous not shown can form a seal between said pistons 10, 39 and said cylinders 8, 30.

[0137] Said pistons 10, 39 may also include an antifriction guide ring 76 made preferably of an abrasion-resistant material such as polytetrafluoroethylene loaded with antifriction particles such as graphite, said ring 76 guiding and centering said pistons 10, 39 in the blind liquid cylinder 8, 30 with which they cooperate.

[0138] By way of example, the working liquid 13 may consist of pure water, water with added glycol to lower the freezing point of said water, or a liquid with a low melting point such as ethanol.

[0139] It should also be noted that the static frame 40 can be fixed or placed on the floor of a residential, commercial or industrial building 121, while the working gas 5 can be atmospheric air or be made up of any other gas such as pure nitrogen, helium, argon, or carbon dioxide, said gas being preferably selected for its chemical neutrality, its thermodynamic performance, and its ability to promote heat exchanges in particular with the working liquid 13, with the first and second means of heat exchange and accumulation of compressor 16, 70, and with the first and second means of heat exchange and accumulation of expansion valve 139, 59.

[0140] The chemical neutrality of the working liquid 13 and the working gas 5 makes it possible in particular to prevent corrosion of the internal components of the grouped mechanical-liquid piston heat pump 1 according to the invention, and the development of microorganisms.

[0141] It is noted that no limit is set on the number of blind liquid cylinders of compressors 8 and on the number of blind liquid cylinders of expansion valves 30.

[0142] As shown in Figures 3 to 7, 9 and 13 to 15, the grouped mechanical-liquid piston heat pump 1 according to the invention also comprises at least one first compressor gas and liquid reservoir 14 which is connected to the first hydraulic variable volume of the compressor 12 by a communication conduit 15, such that said reservoir 14 fills mostly or totally with working liquid 13 when the first hydraulic variable volume of the compressor 12 is minimal, said reservoir 14 fills partially or totally with working gas 5 when the first hydraulic variable volume of the compressor 12 is maximal, the variation in the volume of the working gas 5 contained in the first compressor gas and liquid reservoir 14 defining, on the one hand, a pneumatic variable volume of the compressor 2 and being, on the other hand,approximately equal to the volume variation of the working fluid 13 contained in the first hydraulic variable volume of the compressor 12, according to the principle of communicating vessels.

[0143] Similarly, it has been shown in Figures 3 to 7 and in Figures 13 to 15 that the grouped mechanical-liquid piston heat pump 1 according to the invention also comprises at least one second compressor gas and liquid reservoir 29 which is connected to the second hydraulic variable volume of the compressor 134 by a communication conduit 15, such that said reservoir 29 fills mostly or totally with working liquid 13 when the second hydraulic variable volume of the compressor 134 is minimal, said reservoir 29 fills partially or totally with working gas 5 when the second hydraulic variable volume of the compressor 134 is maximal, the variation in the volume of the working gas 5 contained in the second compressor gas and liquid reservoir 29 defining, on the one hand, a pneumatic variable volume of the compressor 2 and being, on the other hand, approximately equal to the variation in the volume of the working liquid 13 contained in the second variable hydraulic volume of compressor 134 according to the principle of communicating vessels.

[0144] Figures 3 to 5 and Figures 8 to 11 show that the grouped mechanical-liquid piston heat pump 1 according to the invention also comprises at least one blind liquid cylinder of expansion valves 30 which is directly or indirectly integral with the static frame 40, the ends of which are sealed by a sealed termination of an expansion valve cylinder 78, and in which at least one double-acting hydraulic piston of expansion valves 39 can translate in a sealed manner, said piston 39 having, on the one hand, at least one first axial face of an expansion valve piston 43 which forms with said cylinder 30 and one of the sealed terminations of an expansion valve cylinder 78 a first variable hydraulic volume of an expansion valve 44, and on the other hand, at least one second axial face of an expansion valve piston 45 which forms with said cylinder 30 and the other sealed termination of an expansion valve cylinder 78 a second variable hydraulic volume of an expansion valve 46,the two said variable hydraulic volumes 44, 46 being wholly or partly filled with a working fluid 13. ,

[0145] It has been shown in Figures 3 to 6 and in Figures 8 and 9 that the grouped mechanical-liquid piston heat pump 1 according to the invention also comprises at least one first expansion valve gas and liquid reservoir 50 which is connected to the first hydraulic variable volume of the expansion valve 44 by a communication conduit 15, such that said reservoir 50 fills mostly or totally with working liquid 13 when said first hydraulic variable volume of the expansion valve 44 is minimal, said reservoir 50 fills partially or totally with working gas 5 when said first hydraulic variable volume of the compressor 44 is maximal, the variation in the volume of the working gas 5 contained in the first expansion valve gas and liquid reservoir 50 defining, on the one hand, a pneumatic variable volume of the expansion valve 136 and being, on the other hand,approximately equal to the volume variation of the working fluid 13 contained in the first hydraulic variable volume of the pressure regulator 44.

[0146] In Figures 3 to 5 and in [Fig. 8], it can be seen that the mechanical-liquid piston heat pump 1 according to the invention also comprises at least one second expansion valve gas and liquid reservoir 55 which is connected to the second hydraulic variable volume of the expansion valve 46 by a communication conduit 15, such that said reservoir 55 fills mostly or totally with working liquid 13 when the second hydraulic variable volume of the expansion valve 46 is minimal, said reservoir 29 fills partially or totally with working gas 5 when said second hydraulic variable volume of the expansion valve 46 is maximal, the variation in the volume of the working gas 5 contained in the second expansion valve gas and liquid reservoir 55 defining, on the one hand, a pneumatic variable volume of the expansion valve 136 and being, on the other hand, approximately equal to the variation in volume of the working fluid 13 contained in the second hydraulic variable volume of the expansion valve 46.

[0147] It is noted that the maximum acceleration and deceleration to which the working liquid 13 contained in the first and second compressor gas and liquid tanks 14, 29 and in the first and second regulator gas and liquid tanks 50, 55 are subjected must preferably remain below that of Earth's gravity, so that said liquid 13 is not subjected to any cavitation phenomenon or excessive mixing with the working gas 5 which is also contained in said tanks 14, 29, 50, 55.

[0148] It is also noted that a passivator in the form of a perforated or folded sheet metal or a solid structure, permeable or not, may be provided in said tanks 14, 29, 50, 55, in order to avoid excessive turbulence of the working liquid 13 contained in said tanks 14, 29, 50, 55.

[0149] It is noted in figures 3 to 5, 11, and 13 to 15 that the grouped mechanical-liquid piston heat pump 1 according to the invention comprises first compressor heat exchange and accumulation means 16 which are housed in the first compressor gas and liquid reservoir 14 and second compressor heat exchange and accumulation means 59 which are housed in the second compressor gas and liquid reservoir 29, said means 16, 59 each being able to mainly take heat from the working gas 5 which is contained in the reservoir 14, 29 in which they are housed, and temporarily store said heat, this before transferring the latter to the working liquid 13 which is also contained in said reservoir 14, 29.

[0150] Similarly, it is noted in Figures 3 to 5 and in [Fig.8] that the grouped mechanical-liquid piston heat pump 1 according to the invention comprises first means for heat exchange and accumulation of expansion valve 139 which are housed in the first gas and liquid expansion valve reservoir 50 and second means for heat exchange and accumulation of expansion valve 70 which are housed in the second gas and liquid expansion valve reservoir 55, said means 139, 70 each being able to mainly take heat from the working liquid 13 which is contained in the reservoir 50, 55 in which they are housed, and temporarily store said heat, this before releasing the latter to the working gas 5 which is also contained in said reservoirs 50, 55.

[0151] As illustrated in Figures 3 to 5 and [Fig. 11], the grouped mechanical-liquid piston heat pump 1 according to the invention also comprises first heat export means 17 located inside and / or outside the first compressor gas and liquid reservoir 14 and second heat export means 73 located inside and / or outside the second compressor gas and liquid reservoir 29, said means 17, 73 taking heat directly or indirectly respectively from the first heat exchange and heat storage means of compressor 16 and to the second means of exchange and accumulation of heat of compressor 59 on the one hand, and / or to the working liquid 13 and / or to the working gas 5 which are contained in whole or in part in said tanks 14, 29 on the other hand, said heat being then transferred to heating means 18 external to said tanks 14, 29.

[0152] The heating means 18 shown in figures 3 to 5 may take the form of a heated and cooled floor 106 installed in a commercial or residential building 121, or of a fan coil unit known in itself.

[0153] The said means 18 can also take the form of a ground-water or water-water exchanger arranged outdoors 122, according to the principles ordinarily adopted for geothermal heat pumps.

[0154] In Figures 3 to 5 and in [Fig. 8], it has been shown that the grouped mechanical-liquid piston heat pump 1 according to the invention comprises first heat-importing means 138 housed inside and / or outside the first expansion valve gas and liquid reservoir 50 and second heat-importing means 74 housed inside and / or outside the second expansion valve gas and liquid reservoir 55, said means 138, 74 directly or indirectly supplying heat respectively to the first expansion valve heat exchange and storage means 139 and to the second expansion valve heat exchange and storage means 70 on the one hand, and / or to the working liquid 13 and / or the working gas 5 contained in whole or in part in said reservoirs 50, 55 on the other hand, said heat having been previously taken from cooling means 19 external to said reservoirs 50, 55.

[0155] It is noted that the cooling means 19 can take the form of an air-water exchanger 107 placed outside 122 of a building 121, and through which atmospheric air is forced to pass by at least one motor-fan 108.

[0156] The said means 19 can also take the form of a ground-water or water-water exchanger arranged outdoors 122, according to the principles ordinarily adopted for geothermal heat pumps.

[0157] It is noted in Figures 3 to 6 and in Figures 13 to 15 that the grouped mechanical-liquid piston heat pump 1 according to the invention also includes compressor filling means 20 which permit or prohibit the passage of working gas 5 from a compressor inlet plenum 21 to the first compressor gas and liquid reservoir 14 via at least one inlet port 6 while other compressor filling means 20 permit or prohibit the passage of working gas 5 from said plenum 21 or from another compressor inlet plenum 21 to the second compressor gas and liquid reservoir 29 via at least one other inlet port 6.

[0158] Similarly, and as always shown in Figures 3 to 6 and in Figures 13 to 15, the grouped mechanical-liquid piston heat pump 1 according to the invention also includes compressor draining means 22 which permit or prohibit the passage of working gas 5 from the first compressor gas and liquid reservoir 14 to a compressor discharge plenum 62 via at least one outlet port 7 while other compressor draining means 22 permit or prohibit the passage of working gas 5 from the second compressor gas and liquid reservoir 29 to said plenum 62 or to another compressor discharge plenum 62 via at least one other outlet port 7.

[0159] It has been shown in Figures 3 to 6 that the grouped mechanical-liquid piston heat pump 1 according to the invention also includes expansion valve filling means 140 which permit or prohibit the passage of working gas 5 from an expansion valve inlet plenum 142 to the first expansion valve gas and liquid reservoir 50 via at least one inlet port 6, while other expansion valve filling means 140 permit or prohibit the passage of working gas 5 from said plenum 142 or from another expansion valve inlet plenum 142 to the second expansion valve gas and liquid reservoir 55 via at least one other inlet port 6.

[0160] Similarly, Figures 3 to 6 show that the grouped mechanical-liquid piston heat pump 1 according to the invention also includes expansion valve drain means 141 which permit or prevent the passage of working gas 5 from the first expansion valve gas and liquid reservoir 50 to an expansion valve discharge plenum 143 via at least one outlet port 7 while other expansion valve drain means 141 permit or prevent the passage of working gas 5 from the second expansion valve gas and liquid reservoir 55 to said plenum 143 or to another expansion valve discharge plenum 143 via at least one other outlet port 7.

[0161] Figures 3 to 5 and Figures 10 to 12 show that the grouped mechanical-liquid piston heat pump 1 according to the invention comprises a compressor connecting rod 11 which is integral with the double-acting hydraulic piston of compressors 10, which passes in a sealed manner through at least one of the sealed terminations of compressor cylinder 135 and which is approximately parallel to the longitudinal axis of said piston 10 and of the blind liquid cylinder of compressors 8.

[0162] In a similar manner shown in Figures 3 to 5 and in Figures 8, 10 and 11, the grouped mechanical-liquid piston heat pump 1 according to the invention also includes a connecting rod of expansion valves 75 which is integral with the double-acting hydraulic piston of expansion valves 39, which passes in a sealed manner through at least one of the sealed terminations of the expansion cylinder 78, and which is approximately parallel to the longitudinal axis of said piston 39 and of the blind liquid cylinder of expansion valves 30.

[0163] It has been shown in Figures 3 to 5 and in Figures 10 to 12 that the grouped liquid-mechanical piston heat pump 1 according to the invention also comprises means of compressor piston guide 23 which maintain the double-acting hydraulic piston of compressors 10 and the connecting rod of compressors 11 parallel to the blind liquid cylinder of compressors 8, regardless of the position of said piston 10 in said cylinder 8.

[0164] In Figures 3 to 5 and in Figures 10 and 11, it has also been shown that the grouped mechanical-liquid piston heat pump 1 according to the invention comprises piston guiding means of expansion valves 77 which maintain the double-acting hydraulic piston of expansion valves 39 and the connecting rod of expansion valves 75 parallel to the blind liquid cylinder of expansion valves 30, regardless of the position of said piston 39 in said cylinder 30.

[0165] Figures 3 to 8 and Figures 10 and 11 show that the grouped mechanical-liquid piston heat pump 1 according to the invention comprises means for actuation of connecting rods 144 through which at least one drive motor 27 imparts, on the one hand, to the connecting rod of compressors 11 a reciprocating longitudinal translational movement parallel to the axis of the blind liquid cylinder of compressors 8, and on the other hand, to the connecting rod of expansion valves 75 a reciprocating longitudinal translational movement parallel to the axis of the blind liquid cylinder of expansion valves 30.

[0166] It is noted that the drive motor 27 can be electric, internal or external combustion thermal, hydraulic, pneumatic, or of any type known to those skilled in the art.

[0167] As can be seen in Figures 3 to 5 and in [Fig.7], the grouped mechanical-liquid piston heat pump 1 according to the invention comprises mechanical energy storage means 28 which can alternately take and give mechanical energy to said actuating means 144 or to said rods 75, 11, said means 28 being directly or indirectly connected to the actuating means of connecting rods 144 or being directly or indirectly connected to the connecting rod of expansion valves 75 or to the connecting rod of compressors 11.

[0168] It is noted that the means of storing mechanical energy 28 can be inertial, pneumatic, electrical, gravitational, or of any type known or yet to come.

[0169] As can be seen in Figures 3 to 5 and in Figures 7, 8, 10 and 11, according to an alternative embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, the means for actuation of connecting rods 144 may consist of a crankshaft 24 which can rotate in at least one shaft bearing 25 which is directly or indirectly integral with the static frame 40, said crankshaft 24 having at least one crank 26 around which is articulated a connecting rod head 145 of an actuating connecting rod 165, the latter also comprising a foot of connecting rod 146 which articulates, depending on the case, either with the connecting rod of compressors 11, or with the connecting rod of expansion valves 75.

[0170] It is noted that the shaft bearing 25, the connecting rod head 145, and the connecting rod foot 146 can receive a roller bearing 105, a ball bearing or a needle bearing known per se.

[0171] As a variant of the grouped mechanical-liquid piston heat pump 1 according to the invention shown in figures 6 to 11, the crankshaft 24 may have two cranks 26, the first of said cranks 26 being connected by a first actuating rod 165 to the connecting rod of compressors 11 while the second of said cranks 26 is connected by a second actuating rod 165 to the connecting rod of expansion valves 75 so that the connecting rod of compressors 11 and the connecting rod of expansion valves 75 are simultaneously put into reciprocating longitudinal translation by the same drive motor 27 and / or by the same mechanical energy storage means 28, said motor 27 and said means 28 directly or indirectly driving the crankshaft 24 in rotation.

[0172] In this case and as shown in figures 6 to 12, the connecting rod foot 146 can articulate, as the case may be, with the connecting rod of compressors 11 or with the connecting rod of regulators 75 by means of a low-friction connecting hook 147 which is integral with said rod 11, 75.

[0173] Advantageously and as detailed particularly in [Fig. 12], the connecting arm 147 may include a connecting arm yoke 148 which is traversed by a connecting arm axis 155 which is perpendicular, as the case may be, to the connecting rod of compressors 11 or to the connecting rod of expansion valves 75, and around which are articulated on the one hand, a connecting rod foot bearing 149 which includes the connecting rod foot 146 which may advantageously be made of a ball or roller bearing known per se, and at least one connecting arm roller 150 of ball or roller known per se which rolls on at least one connecting arm bearing race 41 which is parallel, as the case may be, to the blind liquid cylinder of compressors 8 or to the blind liquid cylinder of expansion valves 30, and which is directly or indirectly integral with said cylinder 8, 30.

[0174] As a technological equivalent, the cross yoke 148 can be integral with the actuating rod 146 in place of the connecting rod foot 146, while the compressor connecting rod 11 or the expansion rod 75 can receive a bearing or a bushing.

[0175] It is noted that the radial forces to which the cross roller 150 is subjected are equal to a part of the axial force received by the actuating rod 165 when the latter is not perfectly parallel, as the case may be, to the blind liquid cylinder of compressors 8 or to the blind liquid cylinder of expansion valves 30.

[0176] According to another variant of the grouped mechanical-liquid piston heat pump 1 according to the invention shown in [Fig. 1], the first means of exchange and compressor heat storage means 16 and / or second compressor heat exchange and storage means 59 and / or first expansion valve heat exchange and storage means 139 and / or second expansion valve heat exchange and storage means 70 may consist of a porous medium 32 which has porosities 33 into which working liquid 13 and working gas 5 alternately enter and exit.

[0177] By way of example, the porous medium 32 may consist of porous ceramic, a ceramic or metal structure, or a metallic straw made of copper or aluminum.

[0178] Figures 3 and 5 show that the first heat export means 17 can consist of a circulating portion of the working fluid 13 which exits the first hydraulic variable volume of the compressor 12 and / or the first gas and fluid reservoir of the compressor 14 via a liquid outlet duct 34, said circulating portion then returning to said first volume 12 and / or to said first reservoir 14 via a liquid inlet duct 35, this after having directly or indirectly transferred heat to the heating means 18

[0179] Similarly, Figures 3 and 5 show that the second heat export means 73 can consist of a circulating portion of the working fluid 13 which exits the second hydraulic variable volume of the compressor 134 and / or the second gas and fluid tank of the compressor 29 via a liquid outlet duct 34, said circulating portion then returning to said second volume 134 and / or to said second tank 29 via a liquid inlet duct 35, this after having directly or indirectly transferred heat to the heating means 18.

[0180] In these last two cases, it is noted in figures 3 and 5 that the circulating part of the working liquid 13 can advantageously transfer heat to the heating means 18 by means of a secondary heating heat exchanger 153 which can be plate, tubular, or of any type known to those skilled in the art.

[0181] Figures 3 and 5 show that the first means of heat import 138 can also consist of a circulating part of the working liquid 13 which exits the first hydraulic variable volume of the expansion valve 44 and / or the first gas and liquid reservoir of the expansion valve 50 via a liquid outlet conduit 34 to return to said first volume 44 and / or to said first reservoir 50 via a liquid inlet conduit 35, this after having directly or indirectly taken heat from the cooling means 19.

[0182] Similarly, the second heat import means 74 as shown in Figures 3 and 5 can also consist of a circulating portion of the working fluid 13 which exits the second hydraulic variable volume of the expansion valve 46 and / or the second gas and liquid reservoir of the expansion valve 55 via a liquid outlet conduit 34 for return to said second volume 46 and / or to said second reservoir 55 via a liquid inlet conduit 35, this after having directly or indirectly taken heat from the cooling means 19.

[0183] In these last two cases, it is noted in figures 3 and 5 that the circulating part of the working liquid 13 can advantageously take heat from the cooling means 19 by means of a secondary cooling heat exchanger 154 which can be plate, tubular, or of any type known to those skilled in the art.

[0184] Figures 4, 9 and 11 show that according to a particular embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, the first heat export means 17 can consist of at least one heat exchanger duct 36 housed in the first compressor gas and liquid reservoir 14 and in which circulates a heat transfer fluid 37 which exports heat taken from the first compressor heat exchange and storage means 16 on the one hand, and / or from the working fluid 13 and / or from the working gas 5 contained in the first compressor gas and liquid reservoir 14 on the other hand, to the heating means 18, via heat transport ducts 38.

[0185] It is noted that the heat exchanger duct 36 can, as the case may be, form in itself the first and second means of heat exchange and accumulation of compressor 16, 59 or the first and second means of heat exchange and accumulation of expansion valve 139, 70.

[0186] By way of example, the heat exchanger duct 36 can take the form of a coil of copper 109 or aluminum pipe, whereas the heat transport ducts 38 can be coated with thermal insulation.

[0187] It is noted that the coils or layers that can constitute the heat exchanger conduit 36 ​​can be held in place in the first or second compressor gas and liquid tank 14, 29 or in the first or second expansion valve gas and liquid tank 50, 55 and with respect to each other by retaining plates or by separation baffles which can constitute baffles and / or passage restrictions creating jets of working liquid 13 and / or working gas 5 when said liquid 13 and / or said gas 5 passes through said restrictions.

[0188] In addition, the heat exchanger duct 36 can receive external fins which increase its contact surface with the working liquid 13 or the working gas 5.

[0189] Figures 4 and 11 show that, according to another particular embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, the second heat export means 73 can also consist of at least one heat exchanger duct 36 housed in the second compressor gas and liquid reservoir 29 and in which a heat transfer fluid 37 circulates which exports the heat taken from the second means of heat exchange and accumulation of compressor 59 on the one hand, and / or from the working liquid 13 and / or from the working gas 5 contained in the second compressor gas and liquid reservoir 29 on the other hand, to the heating means 18, via heat transport ducts 38.

[0190] Similarly and as shown in Figures 4, 8, 9 and 11, the first heat import means 138 can also consist of at least one heat exchanger duct 36 housed in the first expansion valve gas and liquid reservoir 50 and in which circulates a heat transfer fluid 37 which imports heat from the cooling means 19 to the first expansion valve heat exchange and storage means 139 on the one hand, and / or the working fluid 13 and / or the working gas 5 contained in the first expansion valve gas and liquid reservoir 50 on the other hand, via heat transport ducts 38.

[0191] Similarly and as shown in Figures 4, 8 and 11, the second heat import means 74 can also consist of at least one heat exchanger duct 36 housed in the second expansion valve gas and liquid reservoir 55 and in which circulates a heat transfer fluid 37 which imports heat from the cooling means 19 to the second expansion valve heat exchange and storage means 70 on the one hand, and / or the working fluid 13 and / or the working gas 5 contained in the second expansion valve gas and liquid reservoir 55 on the other hand, via heat transport ducts 38.

[0192] As an alternative embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, it has been shown in [Fig.4] that the first means for exchanging and storing compressor heat 16 and / or the second means for exchanging and storing compressor heat 59 can consist of at least one liquid spray nozzle 71 supplied by a liquid spray pump 72, said nozzle 71 being able, as appropriate, to atomize working liquid 13 into fine droplets in the internal volume of the first compressor gas and liquid reservoir 14 or in the internal volume of the second compressor gas and liquid reservoir 29.

[0193] Similarly, [Fig.4] illustrates that the first means for heat exchange and accumulation of regulator 139 and / or the second means for heat exchange and accumulation of regulator 70 can consist of at least one liquid spray nozzle 71 supplied by a liquid spray pump 72, said nozzle 71 being able, as appropriate, to atomize working liquid 13 into fine droplets in the internal volume of the first regulator gas and liquid reservoir 50 or in the internal volume of the second regulator gas and liquid reservoir 55.

[0194] It is noted that the number, position, and orientation of the liquid spray nozzles 71 are not limited and are provided so that the atomized working liquid 13 exposes the working gas 5 to a large developed surface area for heat exchange, while the entrainment speed of said gas 5 by said liquid 13 also promotes as much as possible the heat exchange between said gas 5 and said liquid 13.

[0195] It is noted that the liquid spray pump 72 may be one or more piston, gear, turbine or of a type known to those skilled in the art.

[0196] The liquid spray pump 72 can for example consist of a piston which is directly or indirectly driven by a cam driven in rotation by the crankshaft 24, the profile of said cam being calculated so that the atomization of the working liquid 13 begins at the opportune angular moment of rotation of said shaft 24, and for an optimal angular duration and according to an optimal intensity variation law.

[0197] It is noted that preferably, the liquid spray pump 72 draws working liquid 13 from the same volume into which it discharges said liquid 13 via the liquid spray nozzle 71, so that the pressure difference between the inlet and outlet of said pump 72 is minimal.

[0198] As another embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, it has been shown in Figures 5 to 7, in [Fig.9], and in Figures 13 to 15 that the first means for exchanging and storing compressor heat 16 and / or the second means for exchanging and storing compressor heat 59 may consist of a rotary liquid atomizer 158 which comprises a rotary atomizing cylinder 159 pierced with radial atomizing orifices 160, an atomizer motor 161 driving said cylinder 159 in rotation sufficiently rapid so that the latter draws working liquid 13 into its axial end by centrifugal force and / or by means of a pumping turbine 162, and radially discharges said liquid 13 in the form of fine droplets into the internal volume of the first compressor gas and liquid reservoir 14 if said atomizer 158 is housed in said first reservoir 14, or into the internal volume of the second compressor gas and liquid reservoir 29 if said atomizer 158 is housed in said second reservoir 29, via the radial atomization ports 160. .

[0199] As can be seen in [Fig.8] and 9, the atomizer motor 161 can advantageously drive the rotating atomizing cylinder 159 by means of a magnetic coupling 124 with a bell or disc known per se, such as those marketed for example by the German company "DST".

[0200] Similarly, it has been shown in Figures 5 to 9 that the first means for heat exchange and accumulation of expansion valve 139 and / or the second means for heat exchange and accumulation of expansion valve 70 can consist of a rotary liquid atomizer 158 which includes a perforated rotary atomizing cylinder 159 radial atomizing ports 160, an atomizer motor 161 driving said cylinder 159 in rotation sufficiently fast so that the latter draws working liquid 13 into its axial end by centrifugal effect and / or by means of a pumping turbine 162, and radially discharges said liquid 13 in the form of fine droplets into the internal volume of the first gas and regulator liquid reservoir 50 if said atomizer 158 is housed in said first reservoir 50, or into the internal volume of the second gas and regulator liquid reservoir 55 if said atomizer 158 is housed in said second reservoir 55, via the radial atomizing ports 160.

[0201] As can be seen in [Fig.5], part of the working liquid 13 drawn in by the axial end of the rotating atomizing cylinder 159 can come from a suction sleeve 163 connected, as appropriate, either to a secondary heating heat exchanger 153 or to a secondary cooling heat exchanger 154.

[0202] This particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention avoids the need for an additional circulator to circulate the working liquid 13 through said secondary exchangers 153, 154, and makes it possible to increase the temperature difference between said liquid 13 and the working gas 5 at the time of atomization of said liquid 13.

[0203] In Figures 3 to 5 and in Figures 10 and 11, it has been shown that the piston guiding means of compressors 23 and / or the piston guiding means of expansion valves 77 can consist of at least one sliding pivot joint 47 formed on the one hand, between an external cylindrical surface 48 which is present in the connecting rod of compressors 11 and the connecting rod of expansion valves 75, and on the other hand, a guide orifice 49 provided in the sealed termination(s) of compressor cylinder 135 through which the connecting rod of compressors 11 passes in the case of the latter 11, or a guide orifice 49 provided in the sealed termination(s) of expansion cylinder 78 through which the connecting rod of expansion valves 75 passes in the case of said connecting rod of expansion valves 75.

[0204] In figures 8, 10 and 11, it was specified that the sliding pivot joint 47 may include an articulated connecting tube 9 which has at one of its ends a sealed ball joint of rod 79 which articulates as appropriate around the connecting rod of compressors 11 or around the connecting rod of expansion valves 75, said articulated tube 9 having at its other end a sealed ball joint of termination 80 which articulates as appropriate with the sealed termination of compressor cylinder 135 or with the corresponding sealed termination of expansion cylinder 78.

[0205] As can be seen in Figures 3 to 5, in [Fig. 8], and in Figures 10 to 12, the piston guiding means of compressors 23 and / or the piston guiding means of expansion valves 77 can consist of a guide skirt 57 arranged around the periphery of the double-acting hydraulic piston of compressors 10 or around the periphery of the double-acting hydraulic piston of expansion valves 39, said skirt 57 being able to translate with little clearance in the blind liquid cylinder of compressors 8 or in the blind liquid cylinder of corresponding expansion valves 30.

[0206] As an alternative embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, the compressor filling means 20 and / or the compressor draining means 22 may consist of at least one compressor valve 52 as mentioned in [Fig.3] and / or at least one piloted compressor valve 53 as shown in Figures 3 to 5, in [Fig.9] and in Figures 13 to 15, while in operation, the working gas 5 is expelled from the first compressor gas and liquid reservoir 14 and from the second compressor gas and liquid reservoir 29 to the compressor discharge plenum 62 under a pressure greater than that under which it was previously introduced into said first reservoir 14 and said second reservoir 29 via the compressor inlet plenum 21.

[0207] It is noted that the compressor valve 52 can be formed of a simple strip or contact piece returned to a sealed seat by a spring of any type, or be formed of a valve assisted by an electromechanical actuator which cooperates with at least one pressure switch or with a pressure sensor coupled to a computer 120.

[0208] It is also noted that a valve open-hold actuator 81 can be provided which prevents the closing of at least one compressor valve 52 to allow the start-up of the grouped mechanical-liquid piston heat pump 1 according to the invention.

[0209] Advantageously and as shown in Figures 3 to 5 and in [Fig.9], the regulator filling means 140 and / or the regulator emptying means 141 may consist of at least one regulator pilot valve 54 while in operation, the working gas 5 is expelled from the first regulator gas and liquid reservoir 50 via the regulator discharge plenum 143 and from the second regulator gas and liquid reservoir 55 under a pressure lower than that under which it was previously introduced into said first reservoir 50 and said second reservoir 55 via the regulator inlet plenum 142.

[0210] As can be seen in Figures 3 to 9, the compressor discharge plenum 62 can be connected to the expansion valve inlet plenum 142 by a high-pressure gas line 56 such that the working gas 5 exiting the pneumatically variable volumes of the compressor 2 via said compressor discharge plenum 62 is introduced into the pneumatically variable volumes of the expansion valve 136 via said expansion valve inlet plenum 142, while the expansion valve discharge plenum 143 is connected to the compressor inlet plenum 21 by a low-pressure gas line 61 so that the working gas 5 exiting the pneumatic variable volumes of the expansion valve 136 via said expansion valve discharge plenum 143 is introduced into the pneumatic variable volumes of the compressor 2 via said compressor inlet plenum 21.

[0211] Figures 3 to 5 illustrate that the high-pressure gas conduit 56 can communicate with at least one high-pressure gas tank 58.

[0212] In a similar manner shown in figures 3 to 5, the low-pressure gas conduit 61 can communicate with at least one low-pressure gas reservoir 60.

[0213] In Figures 3 to 5, it has been shown that according to a particular embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, the working gas 5 which flows in the high-pressure gas duct 56 can transfer its heat to the working gas 5 which flows in the low-pressure gas duct 61 by means of a counter-current regeneration heat exchanger 152, said exchanger 152 being able to be plate, tube, or of any type known to those skilled in the art.

[0214] It is noted that the regeneration heat exchanger 152 can constitute in itself all or part of the high-pressure gas reservoir 58 and / or the low-pressure gas reservoir 60, whereas according to a particular embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, the volume of said reservoirs 58, 60 can be adjusted by the intrusion of a solid or a liquid into said reservoirs 58, 60

[0215] As illustrated in Figures 3 to 5, in [Fig.9], and in Figures 13 to 15, the compressor inlet plenum 21 and the compressor outlet plenum 62 can be part of a compressor cylinder head 110 which covers the upper part of the first compressor gas and liquid tank 14 and the second compressor gas and liquid tank 29, the latter 14, 29 being themselves positioned mainly above the blind compressor liquid cylinder 8, so that, under the effect of Earth's gravity, the working gas 5 is always first to exit said tanks 14, 29 via said outlet plenum 62 while the working liquid 13 is always first to enter said tanks 14, 29 via said inlet plenum 21.

[0216] Thus, the working liquid 13 always remains essentially below the working gas 5 even if said liquid 13 contains a certain proportion of said gas 5 dissolved or in the form of bubbles.

[0217] As shown in Figures 3 to 5 and [Fig. 9], the regulator inlet plenum 142 and the regulator outlet plenum 143 can similarly form part of a regulator cylinder head 111 which covers the upper part of the first regulator gas and liquid reservoir 50 and the second reservoir gas and expansion liquid 55, the latter 50, 55 being themselves positioned mainly above the blind expansion liquid cylinder 30, so that, under the effect of Earth's gravity, the working gas 5 is always first to exit said tanks 50, 55 via said discharge plenum 143, while the working liquid 13 is always first to enter said tanks 50, 55 via said inlet plenum 142.

[0218] Thus, the working liquid 13 always remains essentially below the working gas 5 even if said liquid 13 contains a certain proportion of said gas 5 dissolved or in the form of bubbles.

[0219] According to a particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention shown in Figures 3 to 5 and particularly visibly in [Fig.7], the mechanical energy storage means 28 can consist of a flywheel 66 made rotationally fixed to the crankshaft 24 by a transmission multiplier 156 with simple gear, epicyclic gear train, chain, belt, hydraulic, electric or any type known to those skilled in the art, so that said flywheel 66 rotates significantly faster than the crankshaft 24.

[0220] According to this particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention, the instantaneous torque variations imposed on the crankshaft 24 by the compression or expansion of the working gas 5 in the first and second compressor gas and liquid tanks 14, 29 and in the first and second expansion valve gas and liquid tanks 50, 55 are mainly absorbed by the inertia of the flywheel 66, so that the torque which resists or drives the drive motor 27 is smoothed out, said motor 27 then being mainly subjected to only the average resisting torque necessary to maintain the crankshaft 24 in regular rotation.

[0221] It should be noted that the flywheel 66 may optionally be enclosed in a vacuum housing. In this case, power transmission to said flywheel 66 can be achieved by contactless magnetic coupling.

[0222] It will also be noted that to facilitate the rotation of the crankshaft 24, the drive motor 27 can be fixedly connected in rotation to the flywheel 66, while a disengageable coupler can be inserted between the assembly formed by said motor 27 and said flywheel 66 on the one hand, and the crankshaft 24 on the other hand, said coupler being able to be magnetic, hydraulic, or of any other type known to those skilled in the art.

[0223] It has been shown in Figures 3 to 5 and in [Fig. 7] that the crankshaft 24 can include a toothed ring 67 which the drive motor 27 drives in rotation via at least one ring drive pinion 68 of which the primitive diameter is smaller than that of said crown 67, the latter 67 and said pinion 68 forming a multiplication gear system 69, said crown 67 and said 68 being able to possibly be replaced by an epicyclic train.

[0224] It has been clearly illustrated in Figures 13 to 15 that the outlet ports 7 which open into the compressor discharge plenum 62 or those which open into the expansion valve discharge plenum 143 can each form an overflow tank 113 in which working fluid 13 can be stored, said tank 113 being arranged so that when the compressor draining means 22 or, as the case may be, the expansion valve draining means 141, allow the passage of working gas 5 via said ports 7, said gas 5 having to pass through said tank 113 before opening, as the case may be, into the compressor discharge plenum 62 or into the expansion valve discharge plenum 143.

[0225] It can be seen in figures 13 to 15 that the overflow tanks 113 formed by the outlet ports 7 of the first compressor gas and liquid tank 14 and those 7 of the second compressor gas and liquid tank 29 can open into the same compressor discharge plenum 62 but are separated by a leveling dike 114 which tends to equalize the working liquid levels 13 in said tanks 113 when the compressor draining means 22 associated with said tanks 14, 29 prevent the passage of working gas 5.

[0226] Similarly, the overflow tanks 113 formed by the outlet ports 7 of the first regulator gas and liquid tank 50 and those 7 of the second regulator gas and liquid tank 55 can open into the same regulator discharge plenum 143 but are also separated by a leveling dike 114 which tends to equalize the working liquid levels 13 in said tanks 113 when the regulator draining means 141 associated with said tanks 50, 55 prohibit the passage of working gas 5.

[0227] As can be seen in Figures 3 to 5, according to a particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention, a working liquid level equalization valve 115 can connect the first compressor gas and liquid tank 14 or the second compressor gas and liquid tank 29 with the first expansion valve gas and liquid tank 50 or the second expansion valve gas and liquid tank 55.

[0228] It is noted that the working fluid level equalization valve 115 can advantageously cooperate with one or more working fluid level sensors 13, not shown here, said sensor(s) being housed for example in the compressor discharge plenum 62 or in the expansion valve discharge plenum 143.

[0229] It is noted that the main source of transfer of working liquid 13 from the compressor gas and liquid tanks 14, 29 to the expansion valve gas and liquid tanks 50, 55 or vice versa is the recondensation of the working liquid 13 which circulates in the high pressure gas line 56, in the low pressure gas line 61, or in the regeneration heat exchanger 152.

[0230] Another source of said working fluid transfer 13 is the expansion or contraction of the latter during changes in operating temperature of the grouped mechanical-liquid piston heat pump 1 according to the invention.

[0231] As an alternative embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, it is noted in [Fig.4] that a defrosting heat reservoir 116 can be provided which is heated by the first heat export means 17 and / or the second heat export means 73 and which can transfer its heat to the cooling means 19.

[0232] In this case, the defrosting heat reservoir 116 can be formed of a heat transfer fluid reservoir 123 connected in parallel with the heat transport duct 38 which carries the heat transfer fluid 37 to the cooling means 19, said fluid 37 being able either to pass through said reservoir 123 before reaching the cooling means 19 to heat the latter, or to bypass said reservoir 123 to reach said means 19 directly.

[0233] It will be noted that it is possible to use the grouped mechanical-liquid piston heat pump 1 according to the invention to heat a domestic hot water tank not shown, according to this same principle, or according to any other related principle.

[0234] HOW THE INVENTION WORKS:

[0235] The operation of the grouped mechanical-liquid piston heat pump 1 according to the invention can be easily understood from the view of figures 1 to 15.

[0236] The objective of said heat pump 1 is in particular to constitute at least one pneumatic variable volume of compressor 2 and at least one pneumatic variable volume of expansion valve 136 in which the heat exchanges are maximized between a working gas 5, for example pure nitrogen, and a working liquid 13, for example ethanol or bioethanol, during the compression or expansion of said gas 5 and this, so that said compression or said expansion is as isothermal as possible, the working liquid 13 which has a high volumetric heat capacity imposing predominantly its temperature on the working gas 5 whose volumetric heat capacity is lower.

[0237] Pure nitrogen does not react with ethanol, is environmentally and health neutral because it makes up seventy-eight percent of the composition of the Earth's atmosphere, is not a greenhouse gas, presents no risk to the stratospheric ozone layer, and is not toxic to humans.

[0238] Ethanol or bioethanol, for its part, also presents no environmental risk, is used in the composition of wines and spirits, and presents little risk of explosion or spontaneous combustion, which explains its use in indoor stoves which have a burner and an ethanol reservoir in one and the same object.

[0239] Ethanol has the advantage of a very long shelf life, of several decades or even centuries in a non-reactive environment, provided that certain materials are avoided for making the heat pump with grouped liquid-mechanical pistons 1 according to the invention such as aluminium or copper if these materials are not coated with a barrier layer that is neutral with respect to ethanol.

[0240] Ethanol also has the advantage of a low melting point of less than one hundred and fourteen degrees Celsius which prevents its solidification in the circuits of the grouped liquid-mechanical piston heat pump 1 according to the invention and in particular in the regeneration heat exchanger 152 exposed to negative temperatures, and a boiling point of more than seventy-nine degrees Celsius which makes it impossible to boil under fifty bars which is the minimum pressure prevailing in said pump 1.

[0241] Ethanol also has superior lubricating capacities to water, but at the expense of its volumetric heat capacity which is about half that of water, which remains acceptable in the context of the grouped liquid-mechanical piston heat pump 1 according to the invention.

[0242] The pressure-volume principle diagrams shown in [Fig.1] show the Carnot heat pump cycle executed by the grouped mechanical-liquid piston heat pump 1 according to the invention and according to a particular embodiment of said pump 1, said cycle being operated partly by the compressor 3 with regard to the emission of heat Q1, and partly by the expansion valve 4 with regard to the absorption of heat Q2.

[0243] As can be easily understood, the upper diagram of [Fig.1] is executed by the compressor 3, which is also shown in Figures 3 to 7 and 9 to 11, while the lower diagram of said [Fig.1] is executed by the expansion valve 4, which is shown in Figures 3 to 7 and 8 to 11, the two said diagrams being virtually linked on [Fig.1] by dashed arrows in order to reconstruct the complete thermodynamic cycle of the heat pump 1.

[0244] The dashed arrows illustrate that the hot working gas 5 at temperature T2, discharged by the compressor 3 under high pressure via its compressor discharge plenum 62, is admitted by the expansion valve 4 via its expansion valve inlet plenum 142, whereas the cold working gas 5 at temperature T1 is discharged by the expansion valve 4 at low pressure via its expansion valve discharge plenum 143 is admitted by the compressor via its compressor inlet plenum 21.

[0245] The heat pump cycle shown in [Fig.1] shows that the compressor 3 therefore admits cold working gas 5 at temperature T1 during its intake stroke EA.

[0246] Having done this, the compressor 3 operates an adiabatic compression AB of the working gas 5 to change the temperature of said gas 5 from cold T1 to hot T2.

[0247] Said adiabatic compression AB is followed by an isothermal compression BC during which the work supplied by the double-acting hydraulic piston of compressors 10 visible in figures 3 to 5 and in figures 10 to 12, is converted into heat Q1 which is exported to the heating means 18, for example a heated-cooled floor 106 or high-temperature radiators not shown, via the first and second heat export means 17, 73, said means 18, 17, 73 being clearly visible in figures 3 to 5.

[0248] This is followed by the discharge CD of the working gas 5 compressed and hot at temperature T2 at the end of the compression stroke, followed by the admission EA of working gas 5 cold at temperature T1 and at low pressure from the expansion valve 4, said admission forming the starting point of a new compression cycle.

[0249] The regulator 4 admits working gas 5 compressed and hot at temperature T2 during its admission stroke FG.

[0250] This done, the expansion valve 4 operates an adiabatic expansion GH of the working gas 5 to change its temperature from hot T2 to cold T1 and to return to the double-acting hydraulic piston of expansion valves 39 part of the work consumed by the double-acting hydraulic piston of compressors 10 during the adiabatic compression AB operated in the compressor 3.

[0251] Said adiabatic expansion GH is followed by an isothermal expansion HI during which the working gas 5 at cold temperature Tl still provides work to the double-acting hydraulic piston of expansion valves 39 visible in figures 3 to 5 and in figures 8 and 10, this while maintaining the temperature of said gas 5 at value Tl by capturing heat Q2 which is imported from the cooling means 19 via the first heat import means 138 and the second heat import means 74, said means 19, 138, 74 being clearly visible in figures 3 to 5.

[0252] The isothermal expansion stroke being completed, there follows the discharge LJ of the working gas 5 at low pressure and cold at temperature T1, followed by the admission FG of the working gas 5 compressed and hot at temperature T2 from the compressor 3, which forms the starting point of a new expansion cycle.

[0253] Figure [2] shows a variant of the heat pump thermodynamic cycle shown in [Fig. 1] and just described, said variant allowing for a setting in more relevant work of the grouped mechanical-liquid piston heat pump 1 according to the invention as shown in figures 3 to 15.

[0254] In [Fig.2], the adiabatic compression of the working gas 5 operated by the compressor 3 to go from the cold temperature T1 to the hot temperature T2 is replaced by the heat input Q3 to the working gas 5 admitted by the compressor 3 from the expansion valve 4, said input coming from the regeneration heat exchanger 152 shown in figures 3 to 5.

[0255] Thanks to said heat exchanger 152, the working gas 5 which flows in the high-pressure gas duct 56 gives its heat to the working gas 5 which flows in the low-pressure gas duct 61.

[0256] Thus, the working gas 5 admitted by the compressor 3 during its stroke DA is already hot at temperature T2, while the working gas 5 admitted by the expansion valve 4 during its stroke EF is already cold at temperature Tl.

[0257] It follows from this particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention that the entire compression and discharge stroke of the working gas 5 of the compressor 3 can be carried out isothermally, without prior heating of said gas 5 by adiabatic compression since said gas 5 is already at hot temperature T2.

[0258] The AB stroke therefore forms from its start an isothermal compression during which the work supplied by the double-acting hydraulic piston of compressors 10 is entirely converted into heat Q1 exported to the heating means 18 via the first heat export means 17 and the second heat export means 73, said means 18, 17, 73 being represented in figures 3 to 5.

[0259] This is followed by the discharge BC of the working gas 5 compressed and hot at temperature T2 at the end of the compression stroke, followed by the admission DA of working gas 5 also hot at temperature T2 and at low pressure from the expansion valve 4, said admission forming the starting point of a new compression cycle.

[0260] As in the case of the compressor 3, the principle of [Fig.2] also applies to the expansion valve 4, that is to say that the entire expansion and discharge stroke of the working gas 5 of the expansion valve 4 can be carried out isothermally, without prior cooling of said gas 5 by adiabatic expansion since said gas 5 is already at a cold temperature Tl at the inlet of said expansion valve 4.

[0261] The stroke FG thus forms, from its origin, an isothermal expansion during which part of the work done by the double-acting hydraulic piston of compressors 10 during compression AB is returned to the double-acting hydraulic piston of expansion valves 39, the two said pistons 10, 39 being mechanically linked to each other, for example by a crankshaft 24, this while maintaining the gas temperature of work 5 to value Tl by supply of heat Q2 imported from the cooling means 19 via the first means of heat import 138 and the second means of heat import 74.

[0262] This is followed by the discharge GH of the cold working gas 5 at temperature Tl and low pressure at the end of the expansion stroke, followed by the admission EF of the compressed and cold working gas 5 at temperature Tl from the compressor 3 via the regeneration heat exchanger 152, which forms the starting point of a new expansion cycle.

[0263] In addition to performing the thermodynamic cycles shown in Figures 1 and 2, the objective of the grouped mechanical-liquid piston heat pump 1 according to the invention is to meet all the conditions necessary to obtain an overall effective efficiency higher than that of conventional refrigerant gas heat pumps.

[0264] For this, the efficiency of the heat exchanges must be maximized between the working gas 5 and the working liquid 13 whether in the first compressor gas and liquid tank 14, in the second compressor gas and liquid tank 29, in the first expansion valve gas and liquid tank 50 or in the second expansion valve gas and liquid tank 55, the efficiency of the heat exchanges must also be maximized in the regeneration heat exchanger 152 between the working gas 5 which flows in the high-pressure gas line 56 and that which flows in the low-pressure gas line 61.

[0265] Similarly, the efficiency of heat exchange must be maximized between the first heat export means 17 and the second heat export means 73 on the one hand, and the heating means 18 on the other hand.

[0266] Similarly, the efficiency of heat exchange must be maximized between the first heat import means 138 and the second heat import means 74 on the one hand, and the cooling means 19 on the other hand.

[0267] To maximize heat exchange between the working gas 5 and the working liquid 13, Figures 5, 8, 9, and 13 to 15 show that the first means for heat exchange and accumulation of compressor 16 and the second means for heat exchange and accumulation of compressor 59, as well as the first means for heat exchange and accumulation of expansion valve 139 and the second means for heat exchange and accumulation of expansion valve 70, can advantageously consist of a rotary liquid atomizer 158 comprising a rotating atomizing cylinder 159 perforated with radial atomizing orifices 160, an atomizer motor 161 driving said cylinder 159 in rapid rotation so that the latter draws working liquid 13 into its axial end by centrifugal force of said liquid 13, and by means of a turbine pumping 162 particularly visible in figures 13 to 15.

[0268] Said rotary liquid atomizer 158 radially discharges working liquid 13 in the form of fine droplets as appropriate, into the first internal volume of the compressor gas and liquid tank 14 or into the second compressor gas and liquid tank 29, or into the first regulator gas and liquid tank 50 or into the second regulator gas and liquid tank 55, via the radial atomizing ports 160, and fills the available space with a mixture of working gas 5 and moving droplets of working liquid 13.

[0269] By rotating in said reservoirs 14, 29, 50, 55, the fine droplets cause the working gas ring 5 formed in said reservoirs 14, 29, 50, 55 to rotate, which allows said droplets to propagate radially from the outside of the rotating atomizing cylinder 159 to the inner peripheral wall of said reservoirs 14, 29, 50, 55 despite a pressure of, for example, only one hundred millibars produced by the rotating atomizing cylinder 159.

[0270] The efficiency of heat exchange depends in particular on the time and the contact surface available for said exchanges to take place, which explains why the heat pump with grouped mechanical-liquid pistons 1 is operated at a low frequency, for example at a maximum of one Hertz for a round trip of the double-acting hydraulic piston of compressors 10 and the double-acting hydraulic piston of expansion valves 39 in their respective cylinders 8, 30, which also leaves all the time necessary for the transfers to take place via the inlet ports 6 and the outlet ports 7 of the compressor 3 and the expansion valve 4 in order to limit the losses by shunting of the working gas 5 when passing through said ports 6, 7.

[0271] This low actuation frequency justifies the use of a flywheel 66 rotating at high speed, for example at three thousand revolutions per minute at the maximum speed of the crankshaft 24 of sixty revolutions per minute.

[0272] The flywheel 66 is particularly visible in Figures 3 to 5 and in [Fig.7], and the instantaneous torque variations imposed on the crankshaft 24 by the compression or expansion of the working gas 5 in the compressor 3 and in the expansion valve 4 are mainly absorbed by the inertia of said flywheel 66, so that the torque which resists or drives the drive motor 27 is smoothed out, said motor 27 then being mainly subjected to the average resisting torque necessary to maintain the crankshaft 24 in regular rotation.

[0273] The said heat exchange efficiency also depends on the pressure and density of the working gas 5, which is why we will take here as an example a heat pump with grouped mechanical-liquid pistons 1 according to the invention whose low pressure found at the beginning of compression and end of expansion is fifty bars, and whose high pressure found at the end of compression and beginning of expansion is one hundred bars.

[0274] The low compression ratio of two to one referred to here and the high operating pressures of the grouped mechanical-liquid piston heat pump 1 according to the invention, are favorable to a high compactness of said pump, to large exchange surfaces during compression and expansion, and to a good regularity of heat power absorbed or emitted respectively by the expansion valve 4 and by the compressor 3 during their expansion or compression stroke.

[0275] The efficiency of the grouped mechanical-liquid piston heat pump 1 according to the invention also depends on the volumetric ratio of its compressor 3 and its expansion valve 4.

[0276] The higher the volumetric ratio, the higher the volumetric efficiency of said compressor 3 and said expansion valve 4, which explains among other things the choice of a liquid piston formed by the working liquid 13 with the first gas and liquid tank of compressor 14, with the second gas and liquid tank of compressor 29, with the first gas and liquid tank of expansion valve 50, and with the second gas and liquid tank of expansion valve 55.

[0277] To benefit from a volumetric ratio close to infinity, as shown particularly in Figures 13 to 15, the outlet ports 7 of the compressor 3 each receive a pilot-operated compressor valve 53 while the outlet ports 7 of the expansion valve 4 each receive a pilot-operated expansion valve 54, said valves 53, 54 cooperating with an overflow tank 113 in order to ensure that a minimum of residual working gas 15 remains in the gas and liquid tanks 14, 29, 50, 55 at the end of the discharge stroke of the compressor 3 and the expansion valve 4.

[0278] Obtaining from the grouped mechanical-liquid piston heat pump 1 according to the invention a breakthrough efficiency compared to conventional refrigerant gas heat pumps also involves minimizing mechanical friction.

[0279] As can be seen in figures 3 to 5, the first axial face of compressor piston 132 and the second axial face of compressor piston 133 of the double-acting hydraulic piston of compressors 10 are antagonistic so that the force received by the connecting rod of compressors 11 results from the sum of the forces applied by the pressure of the working fluid 13 on said axial faces 132, 133.

[0280] As shown in Figures 3 to 5, the first axial face of the regulator piston 43 and the second axial face of the regulator piston 45 are also antagonistic so that the force received by the regulator connecting rod 75 results from the sum of the forces applied by the pressure of the working fluid 13 on said axial faces 43, 45.

[0281] This particular configuration ensures minimal force applied to the actuating means of connecting rods 144, which in this case consist of a shaft with a crank 24 and two connecting rods 165, one for the compressor 3 and the other for the expansion valve 4.

[0282] Indeed, the connecting rod-crank system formed by said shaft 24 and said connecting rods 165 is subjected, on the one hand, only to the difference between the force exerted on the connecting rod of compressors 11 by the first axial face of compressor piston 132 and that exerted on said rod 11 by the second axial face of compressor piston 133 in the case of compressor 3, and on the other hand, only to the difference between the force exerted on the connecting rod of regulators 75 by the first axial face of regulator piston 43 and that exerted on said rod 11 by the second axial face of regulator piston 45 in the case of regulator 4.

[0283] To minimize the mechanical friction generated by the operation of the grouped mechanical-liquid piston heat pump 1 according to the invention and according to the configurations of said pump 1 shown in figures 3 to 12, the double-acting hydraulic piston of compressors 10 and the double-acting hydraulic piston of expansion valves 39 are not subjected to any radial force despite the high axial forces to which they are subjected, resulting from a maximum pressure of, for example, one hundred bars according to this non-limiting example.

[0284] This is all the more necessary as the low speed of translation of the double-acting hydraulic piston of compressors 10 in the blind liquid cylinder of compressors 8 and the low speed of translation of the double-acting hydraulic piston of expansion valves 39 in the blind liquid cylinder of expansion valves 30 does not favour the establishment of a hydrodynamic lubrication regime at the contact interface between said piston 10, 39 and said cylinder 8, 30 with which each cooperates.

[0285] This is also all the more necessary if the working fluid which enters between said piston 10, 39 and said cylinders 8, 30 is water, the latter being of low viscosity and having limited lubricating properties, which is also unfavorable to the establishment of a hydrodynamic lift regime between said pistons 10, 39 and said cylinders 8, 30.

[0286] To avoid subjecting the double-acting hydraulic piston of compressors 10 and the double-acting hydraulic piston of expansion valves 39 to any radial force whatsoever, as can be clearly seen in Figures 10 to 12, the connecting rod actuating means 144, through which the drive motor 27 imparts a reciprocating longitudinal translational motion to the connecting rod of compressors 11 and to the connecting rod of expansion valves 75, are advantageously constituted here, by way of non-limiting example, of a crankshaft 24, the latter having two cranks 26, one of which is articulated with the connecting rod head 145 of an actuating rod 165, the latter also having a connecting rod foot 146 which is articulated around the connecting rod of compressors 11 by means of a connecting arm 147, and the other of which is articulated with the connecting rod head 145 of another actuating arm 165 the latter also comprising a connecting rod foot 146 which is articulated around with the connecting rod of regulators 75 by means of another connecting arm 147.

[0287] This configuration also makes it possible to make the grouped mechanical-liquid piston heat pump 1 according to the invention more compact than that resulting from the variants shown in figures 3 to 5 where the compressor 3 and the expansion valve 4 are aligned, the latter version however having the advantage of a lower torque exerted on the crankshaft 24 and a less need to store mechanical energy via the mechanical energy storage 28.

[0288] It will be noted that, always with a view to minimizing mechanical friction, generated by the operation of the grouped mechanical-liquid piston heat pump 1 according to the invention and from the configuration of said pump 1 shown in figures 6 to 11, the two cranks 26 which receive the crank shaft 24 can advantageously be offset, for example by forty-five degrees, to minimize the exchanges of mechanical energy between said shaft 24 and the flywheel 66.

[0289] Indeed, this forty-five degree offset allows in particular that the resisting torque produced by the compressor 3 on the crankshaft 24 is compensated as much as possible by the driving torque produced by the expansion valve 4 on the same said shaft 24, which effectively limits the exchanges of mechanical energy between said crankshaft 24 and the flywheel 66.

[0290] Said offset of forty-five degrees also makes it possible to limit the pressure variations occurring in the high-pressure gas conduit 56 and in the low-pressure gas conduit 61.

[0291] As can be seen particularly in figures 11 and 12, the connecting arm 147 includes a connecting arm yoke 148 which is traversed by a connecting arm axis 155 which is perpendicular to the connecting rod 11, 75 with which said yoke 148 cooperates and around which are articulated on the one hand, a connecting rod foot bearing 149 which includes the connecting rod foot 146 in the form of a roller bearing 105, and two connecting arm rollers 150 which each roll alternately on two connecting arm bearing tracks 41 parallel to the blind liquid cylinder of compressors 8 and to the blind liquid cylinder of expansion valves 30.

[0292] According to this particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention, the radial forces which result from the obliquity of the actuating rods 165 generated during the rotation of the crankshaft 24 are supported by the two cross rollers 150 positioned on either side of the corresponding cross yoke 148, which limits the friction losses which result from said radial forces.

[0293] It should also be noted in Figures 7, 8, 10 and 11 that the crankshaft 24 is also mounted on roller bearings 105, as well as the shaft which supports the flywheel 66 and the shaft which supports on one side the rotor of the drive motor 27, and on the other side the crown gear 68 integral with said rotor.

[0294] Since the effective coefficient of friction of the roller bearings 105 is very low, they dissipate little energy and have little negative impact on the energy efficiency of the grouped liquid-mechanical piston heat pump 1 according to the invention.

[0295] It should also be noted that the gear systems formed by the various crowns and pinions which constitute a transmission multiplier 156 between the flywheel 66 and the crankshaft 24 are to be precise and of good quality, with the aim of giving them as much as possible a transmission efficiency of more than ninety-nine percent.

[0296] In figures 3 to 7, in [Fig.8] and in figures 13 to 15, it can be seen that the compressor filling means 20 and the compressor emptying means 22 are advantageously made up of piloted compressor valves 53 while the regulator filling means 140 and the regulator emptying means 141 are made up of piloted regulator valves 54.

[0297] This feature makes it easy to switch the grouped mechanical-liquid piston heat pump 1 according to the invention from "heating" mode to "air conditioning" mode without any need to reverse the roles between that of the compressor 3 and that of the expansion valve 4, said compressor 3 being able to assume the function normally occupied by the expansion valve 4, and vice versa.

[0298] If, as we have seen previously, the two cranks 26 which receive the crank shaft 24 are offset by forty-five degrees, said shaft 24 will advantageously rotate in one direction in "heating" mode, and in the opposite direction in "air conditioning" mode.

[0299] For indeed, according to a particular embodiment of the grouped mechanical-liquid piston heat pump 1 according to the invention, nothing physically distinguishes the compressor 3 from the expansion valve 4 except the distribution diagram operated by the compressor pilot valves 53 and the expansion valve pilot valves 54.

[0300] Thus, when the grouped mechanical-liquid piston heat pump 1 according to the invention switches from "heating" mode to "air conditioning" mode, the heating means 18 shown in figures 3 to 5 become the cooling means 19 and vice versa, without it being necessary to interchange the heat transfer fluid circuits which directly or indirectly connect said means to the compressor 3 or the expansion valve 4.

[0301] Because, in fact, the heat transfer fluid of the circuit exposed to the outside 122 of the building 121 is, for example, made up of water with added glycol for protection against freezing, while the heat transfer fluid of the circuit which runs inside building 121 can consist of only pure water, which is less toxic, less corrosive, and cheaper, which is decisive in view of the much larger quantities contained in this latter circuit.

[0302] Thus, the pressure-volume principle diagrams shown in figures 1 and 2 of the thermodynamic cycle of the grouped liquid-mechanical piston heat pump 1 according to the invention remain identical, however, because the compressor filling means 20 and the compressor emptying means 22 are advantageously made up of compressor piloted valves 53, the compressor 3 can perform the lower part of said diagrams normally performed by the expansion valve 4, while the latter can perform the upper part of said diagrams normally performed by the compressor 3.

[0303] The compressor filling means 20 and the compressor emptying means 22, consisting of compressor piloted valves 53, also allow the grouped mechanical-liquid piston heat pump 1 according to the invention to be started.

[0304] Indeed, in order to set the crankshaft 24 in motion, the drive motor 27 must overcome the resisting torque produced by the compressor connecting rod 11 and the expansion connecting rod 75 on the crankshaft 24 while setting the flywheel 66 in motion, which may exceed the maximum torque that said motor 27 can deliver.

[0305] For this purpose, the pilot-operated compressor valves 53 located on the inlet port 6 of the compressor 3 can remain constantly open, as can the pilot-operated expansion valve 54 in order to limit the resisting torque of the crankshaft 24, during the time of the rotation of the latter 24 and of the flywheel 66 with which it cooperates.

[0306] An alternative may consist of a valve or solenoid valve not shown which temporarily connects the high-pressure gas line 56 with the low-pressure gas line 61 to equalize the pressure in the two said lines 56, 61, for the time it takes to move the crankshaft 24 by the drive motor 27.

[0307] It has previously been mentioned that in cooperation with the overflow tanks 113, the pilot-operated compressor valves 53 and the pilot-operated expansion valves 54 make it possible to give the grouped mechanical-liquid piston heat pump 1 according to the invention an infinite volumetric ratio, which is decisive for its efficiency.

[0308] The operation of the overflow tanks 113 is illustrated in Figures 13 to 15, which show the compressor 3 and particularly the compressor pilot valve 53 positioned on the outlet port 7 of the first compressor gas and liquid reservoir 14, said valve 53 constituting the means of draining compressor 22 and ending, in [Fig. 13], in expelling the working gas 5 out of said reservoir 14.

[0309] It is noted in [Fig. 13] that after expelling all of the working gas 5 from the first compressor gas and liquid reservoir 14, some of the working liquid 13 from the previous cycle is also discharged and received by the corresponding overflow tank 113, arranged in the compressor discharge plenum 62.

[0310] This strategy ensures that no residual working gas 5 remains in the first compressor gas and liquid tank 14 before re-admitting working gas 5 via the compressor piloted valve 53 positioned on the inlet port 6 of said first tank 14, said valve 53 forming the compressor filling means 20.

[0311] For indeed, as shown in [Fig.14], the pilot-operated compressor valve 53 positioned on the outlet port 7 remains open a few degrees after the top dead center of the corresponding double-acting hydraulic piston of compressors 10, this in order to re-admit into the first gas and liquid tank of compressor 14 working liquid 5 from the overflow tank 113 which cooperates with said valve 53.

[0312] When the desired quantity of re-admitted working liquid 5 is reached which will be used by the next cycle, the compressor pilot valve 53 positioned on the outlet port 7 closes while the compressor pilot valve 53 positioned on the inlet port 6 opens to allow the working gas charge 5 necessary for the operation of the grouped mechanical-liquid piston heat pump 1 according to the invention to enter.

[0313] A similar principle is used to give the regulator 4 an infinite volumetric ratio, with the detail that at each cycle, the regulator 4 empties completely and alternately the overflow tanks 113 which are positioned at the level of its outlet ports 7 and which are arranged in the discharge plenum of regulator 143.

[0314] The dimension of said tanks 113 is calculated to correspond to the quantity of working liquid 13 to be introduced as appropriate into the first gas and liquid regulator tank 50 or into the second gas and liquid regulator tank 55, this before expelling all of the working gas 5 contained in said tanks 50, 55 each via its outlet port 7.

[0315] Advantageously, a level sensor not shown can measure the level of the working fluid 13 retained in the overflow trays 113 arranged in the discharge plenum of the expansion valve 143 and / or in the discharge plenum of the compressor 62, particularly due to the reversibility of the heat pump. grouped mechanical-liquid pistons 1 according to the invention allowing it to operate indifferently in "heating" mode or in "air conditioning" mode.

[0316] It will be noted that the ethanol chosen here as the working liquid 13 expands strongly under the effect of temperature, and that as such its total volume in the grouped mechanical-liquid piston heat pump 1 can vary significantly.

[0317] Advantageously, the overflow tanks 113 arranged in the compressor discharge plenum 62 can collect the excess volume of said working liquid 13, in this case ethanol, because the level of said liquid 13 in said tanks 113 can vary greatly without prejudice to the operation of the grouped mechanical-liquid piston heat pump 1 according to the invention.

[0318] Therefore, the working liquid level 13 in the overflow tanks 113 arranged in the discharge plenum of the expansion valve 143 must be kept close to constant, the excess of said liquid 13 being transferred from the expansion valve 4 to the compressor 3 by means of a working liquid level equalization valve 115 visible in figures 3 to 5.

[0319] The working liquid level equalization valve 115 can, for example, fleetingly and cyclically connect the lower part of the first expansion valve gas and liquid reservoir 50 with the lower part of the first compressor gas and liquid reservoir 14 when, during the thermodynamic cycle as presented in [Fig.1] or [Fig.2], the pressure prevailing in said first expansion valve gas and liquid reservoir 50 is greater than that prevailing in said first compressor gas and liquid reservoir 14, this in order to maintain the working liquid level 13 in the overflow tanks 113 arranged in the expansion valve discharge plenum 143 close to constant.

[0320] This strategy is made necessary in particular by the fact that during the operation of the grouped mechanical-liquid piston heat pump 1 according to the invention, part of the working liquid 13 which has passed into the vapor state at the outlet of the compressor 3 condenses in the regeneration heat exchanger 152 and returns to the liquid state, which naturally tends to transfer working liquid 13 from the compressor 3 to the expansion valve 4.

[0321] To maximize the efficiency of the grouped mechanical-liquid piston heat pump 1 according to the invention, it is noted in [Fig.4] that advantageously, a partitioned thermo-insulating enclosure 164, made for example of expanded polyurethane plates, thermally insulates the compressor 3 from the expansion valve 4, and insulates the latter 3, 4 from the connecting rod actuation means 144, the drive motor 27 and the mechanical energy storage means 28, said enclosure 164 also thermally separating said heat pump 1 from its external environment.

[0322] We note in [Fig.4] the heating-cooling means of the drive group 125 which connect the thermally insulated compartment which contains the connecting rod actuation means 144, the drive motor 27 and the mechanical energy storage means 28, to the heating means 18 and the cooling means 16.

[0323] The heating-cooling means of the drive group 125 may, for example, consist of a first loop of pure water which surrounds the stator of the electric drive motor 27, said first loop being connected to the circuit of the heating means 18 housed in the building 121, and a second loop of water with added glycol which also surrounds the stator of said motor 27, said second loop being connected to the circuit of the cooling means 16 housed outside 122 of the building 121.

[0324] In “heating” mode, said first loop is activated by an electric circulator 126 or a solenoid valve not shown and recovers the heat emitted by the drive motor 27, in this case electric, by the connecting rod actuation means 144, and by the mechanical energy storage means 28 to transfer said heat to the heating means 18 housed in the building 121.

[0325] In "air conditioning" mode, the second loop is activated by another small electric circulator 126 or a solenoid valve not shown and recovers the heat emitted by the drive motor 27, in this case electric, by the connecting rod actuation means 144, and by the mechanical energy storage means 28 to transfer said heat to the cooling means 19 located outside 122 of the building 121.

[0326] This particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention further maximizes the efficiency of the latter 1 particularly when it operates in "heating" mode, and maintains the electric drive motor 27, the connecting rod actuation means 144, and the mechanical energy storage means 28 at a constant temperature.

[0327] It is understood that according to this particular configuration of the grouped mechanical-liquid piston heat pump 1 according to the invention, almost all of the heat emitted as a result of friction or electromechanical energy losses generated by the drive motor 27, the connecting rod actuation means 144, the mechanical energy storage means 28 as well as those generated by the multiplication gear system 69 and the transmission multiplier 156 are reinjected in "heating" mode into the heating means 18 consisting for example of a heated-cooled floor 106 or high-temperature radiators, or dissipated in "air conditioning" mode outside 122 of the building 121.

[0328] It is noted that the power setting of the grouped mechanical-liquid piston heat pump 1 according to the invention can be achieved either by varying the rotation speed of the crankshaft 24 for example between ten and sixty revolutions per minute by means of, for example, an electrical frequency modulator known per se which supplies the electric drive motor 27, or by playing on the compression ratio of the compressor 3 and the expansion ratio of the expansion valve 4 for example between one point five and two to one, or both.

[0329] The adjustment of said power by the compression ratio of the compressor 3 is carried out by adapting the lift laws of the piloted compressor valves 53 and those of the piloted expansion valves 54, said valves 53, 54 each being actuated in opening and / or closing by a valve actuator 119.

[0330] The setting of the rotation speed of the crankshaft 24, the compression ratio of the compressor 3, and the expansion ratio of the expansion valve 4, are ensured by a computer 120.

[0331] For indeed, all other things being equal, the power of the grouped mechanical-liquid piston heat pump 1 according to the invention is proportional to the rotational speed of its crankshaft 24, which is a first adjustment which allows the computer 120 to adjust said power.

[0332] But in addition to the rotation regime of its crankshaft 24, the more or less delayed and more or less spread lifting of the pilot-operated pressure regulator valves 54 allows the pressure which reigns in the high-pressure gas conduit 56, which is particularly visible in figures 3 to 5, to be adjusted relative to that which reigns in the low-pressure gas conduit 61, also visible in figures 3 to 5.

[0333] This setting is of great importance because the pressure differential in question determines in particular the amount of heat produced by the heat pump 1 at each turn of the crankshaft 24.

[0334] This adjustment is achieved for example by transferring less working gas 5 from the high-pressure gas line 56 to the first gas and liquid regulator 50 and the second gas and liquid regulator 55 during section EF of the diagram of said regulator 4 in [Fig.2], than the compressor 3 transfers during section BC of said diagram, which has the effect of raising the pressure in the high-pressure gas line 56 while lowering the pressure in the low-pressure gas line 61.

[0335] If, on the contrary, the expansion valve 4 transfers more working gas 5 from the high-pressure gas line 56 to the first expansion valve gas and liquid reservoir 50 and the second expansion valve gas and liquid reservoir 55 during section EF of the diagram of said expansion valve 4 in [Fig. 2], than the compressor 3 transfers during In section BC of the said diagram, the pressure in the high-pressure gas duct 56 decreases as the pressure in the low-pressure gas duct 61 increases.

[0336] It will be noted advantageously that the compressor pilot valve and the expansion valve pilot valves 54 can behave both as valves and as flappers, that is to say that they can open under the effect of a pressure differential, in addition to being actuated in opening by their valve actuator 119.

[0337] As such, said valves 53, 54 are advantageously autoclaved and are, during the majority of the time of the thermodynamic cycle shown in [Fig.1] or 2, kept pressed by pressure on their seat which may for example consist of an elastomer or polymer O-ring housed in a groove.

[0338] If, on the other hand, the pressure changes direction, said valves 53, 54 can open without intervention of their valve actuator 119.

[0339] As can be seen in [Fig.4], the grouped mechanical-liquid piston heat pump 1 according to the invention may include a defrosting heat reservoir 116 formed of a hot heat transfer fluid reservoir 123, said reservoir being connected in parallel with the heat transport conduit 38 in which a cold heat transfer fluid 37 circulates, for example water with added glycol, said fluid 37 transporting heat from the cooling means 19 to the first and second heat import means 138, 74 to which it gives said heat.

[0340] After each defrosting cycle of the cooling means 19, the heat transfer fluid reservoir 123 is heated and then kept hot by the first heat export means 17 and / or the second heat export means 73 of the compressor 3, for example by means of a copper coil housed inside said reservoir 123 and in which a hot heat transfer fluid 37 circulates, for example pure water.

[0341] As can be seen in [Fig.4], the first, second and middle heat export ducts 17, 73 each consist of a heat exchanger duct 36 housed respectively in the first and second compressor gas and liquid reservoirs 14, 29.

[0342] As can easily be deduced from [Fig.4], the heat transfer fluid 37 cooled by the expansion valve 4 can either pass through the heat transfer fluid reservoir 123 before reaching the cooling means 19 to heat the latter, or bypass said reservoir 123 to reach said means 19 directly.

[0343] Thus, when the cooling means 19 are covered with frost due to their low temperature, the computer 120 can start the electric circulator 126 placed in series with the heat transfer fluid reservoir 123 so that the hot heat transfer fluid 37 contained in said reservoir 123 reaches said means 19 and fills them completely.

[0344] Immediately afterwards, the circulation of the heat transfer fluid 37 in the heat transport duct 38 which transports said fluid 37 to the cooling means 19 ceases, while the hot heat transfer fluid 37 which fills said means 19 gives its heat to the latter 19 and defrosts said means 19.

[0345] It is noted in [Fig.4] that the electric circulator 126 placed in series with the heat transfer fluid reservoir 123 cooperates with a non-return valve of resistance 127 so that no heat transfer fluid 37 passes through the heat transfer fluid reservoir 123 when said circulator 126 is stopped.

[0346] It should be noted that the grouped mechanical-liquid piston heat pump 1 according to the invention may, in addition to the various components and accessories shown in Figures 3 to 16, include various other devices and accessories such as pressure and / or temperature sensors, a frequency converter for regulating the electrical supply to the electric drive motor 27 sequentially as a function of the angle of the crankshaft 24 or continuously, at least one angular encoder and / or a passage detection sensor which returns to the computer 120 the speed and / or angular position of the crankshaft 24, one or more pumps and / or compressors and / or valves for transferring working gas 5 or working liquid 13 from external sources to the constituent components of said heat pump 1, one or more expansion vessels, circulators, auxiliary pumps, drains, safety elements for persons,pressure limiters or relief valves, or any other equipment known to those skilled in the art that is useful for the proper functioning of said pump 1 according to the invention.

[0347] The grouped mechanical-liquid piston heat pump 1 according to the invention may also include a layer of thermal insulation on all the necessary components, and whatever the nature of said layer which may take the form of flexible or rigid insulating foam or wool, insulating bricks, plates or screens which reflect radiation of any kind.

[0348] The thermal insulation layer can insulate said heat pump 1 and its components from the external environment and / or insulate the compressor 3, which is hot, from the expansion valve 4, which is colder.

[0349] Said heat pump 1 can also receive an acoustic insulation envelope, and its static frame 40 can rest on the ground by means of anti-vibration elastic pads.

[0350] It should also be noted that suspended droplet collectors made of steel wool or stainless steel may be provided in the compressor discharge plenum 62 and / or in the expansion valve discharge plenum 143.

[0351] It should also be noted that the calculator 120 can operate optimization software which adjusts the rotation speed of the crankshaft 24 and the compression ratio of the compressor 3 to regulate the power of the grouped mechanical-liquid piston heat pump 1 according to the invention, but also potentially the rotation speed of the rotating atomizing cylinders 159 of said pump 1 and the rotation speed of the motor-fans 108 of the cooling means 19, as well as the flow rate of the heat transfer fluids of the various internal and external circuits of said pump 1 by regulating the power of various electric circulators 126.

[0352] The software operated by the computer 120 can in particular be connected to the internet network and use artificial intelligence to optimize the operation of the grouped mechanical-liquid piston heat pump 1 according to the invention in order to maximize its efficiency taking into account weather forecasts, the lifestyle habits of the inhabitants of the building 121, and the characteristics of the latter 121 such as its thermal inertia, its insulation, and external contributions to its heating or cooling.

[0353] It is understood that many architectures are applicable to the grouped mechanical-liquid piston heat pump 1 according to the invention, with a blind liquid cylinder of compressors 8 or a blind liquid cylinder of vertical expansion valves 30, a first or second gas and liquid tank of compressor 14, 29 and / or a first and second gas and liquid tank of expansion valve 50, 55 remote and connected to said cylinders 8, 30 by a communication conduit 15 of any geometry and any length whatsoever.

[0354] It is also noted that several blind liquid cylinders of compressor 8 or several blind liquid cylinders of expansion valves 30 can cooperate whose double-acting hydraulic pistons of compressors 10 and double-acting hydraulic pistons of expansion valves 39 are set in motion by common or non-common connecting rod actuating means 144, phased or angularly offset, synchronized or not, said cylinders 8, 30 being able to be juxtaposed, superimposed, mounted head-to-tail, in opposition or in any relative position and orientation whatsoever.

[0355] The possibilities of the grouped mechanical-liquid piston heat pump 1 according to the invention are not limited to the applications which have just been described and it must also be understood that the preceding description has been given only by way of example and that it does not in any way limit the field of said invention which would not be exceeded by replacing the execution details described by any other equivalent.

Claims

1. Demands A heat pump with grouped mechanical-liquid pistons (1) comprising at least one compressor (3) in which at least one pneumatic variable compressor volume (2) is formed, and at least one expansion valve (4) in which at least one pneumatic variable expansion valve volume (136) is formed, each said volume (2, 136) having on the one hand an inlet port (6) through which a working gas (5) can enter and on the other hand an outlet port (7) through which said gas (5) can exit, characterized in that it comprises: • At least one blind liquid cylinder of compressors (8) which is directly or indirectly attached to a static frame (40), each end of which is sealed by a sealed termination of a compressor cylinder (135), and in which at least one double-acting hydraulic compressor piston (10) can translate in a sealed manner, which has, on the one hand, at least one first axial face of a compressor piston (132) which forms with said cylinder (8) and one of the sealed terminations of a compressor cylinder (135) a first hydraulic variable compressor volume (12), and on the other hand, at least one second axial face of a compressor piston (133) which forms with said cylinder (8) and the other sealed termination of a compressor cylinder (135) a second hydraulic variable compressor volume (134), the two said hydraulic variable volumes (12, 134) being wholly or partly filled with a working fluid (13); • At least one first compressor gas and fluid reservoir (14) which is connected to the first hydraulic variable volume of the compressor (12) by a communicating conduit (15), such that said reservoir (14) fills mostly or totally with working fluid (13) when the first hydraulic variable volume of the compressor (12) is minimal, said reservoir (14) fills partially or totally with working gas (5) when the first hydraulic variable volume of the compressor (12) is maximal, the variation in the volume of the working gas (5) contained in the first gas reservoir and compressor fluid (14) defining, on the one hand, a pneumatic variable volume of compressor (2) and being, on the other hand, approximately equal to the volume variation of the working fluid (13) contained in the first hydraulic variable volume of compressor (12);At least one second compressor gas and liquid reservoir (29) which is connected to the second hydraulic variable volume of the compressor (134) by a communication conduit (15), such that said reservoir (29) fills mostly or totally with working liquid (13) when the second hydraulic variable volume of the compressor (134) is minimal, said reservoir (29) fills partially or totally with working gas (5) when the second hydraulic variable volume of the compressor (134) is maximal, the variation in the volume of the working gas (5) contained in the second compressor gas and liquid reservoir (29) defining, on the one hand, a pneumatic variable volume of the compressor (2) and being, on the other hand, approximately equal to the variation in the volume of the working liquid (13) contained in the second hydraulic variable volume of the compressor (134); At least one blind liquid cylinder of pressure regulators (30) which is directly or indirectly integral with the static frame (40), the ends of which are sealed by a pressure regulator cylinder termination (78), and in which at least one double-acting hydraulic pressure regulator piston (39) can move in a sealed manner, said piston (39) having, on the one hand, at least one first axial face of a pressure regulator piston (43) which forms with said cylinder (30) and one of the sealed ends of a pressure regulator cylinder (78) a first variable hydraulic pressure regulator volume (44), and on the other hand, at least one second axial face of a pressure regulator piston (45) which forms with said cylinder (30) and the other sealed end of a pressure regulator cylinder (78) a second variable hydraulic pressure regulator volume (46), the two said volumes hydraulic variables (44, 46) being wholly or partly filled with a working fluid (13); At least one first expansion valve gas and liquid reservoir (50) which is connected to the first hydraulic expansion valve variable volume (44) by a communication conduit (15), such that said reservoir (50) fills mostly or totally with working liquid (13) when said first hydraulic expansion valve variable volume (44) is minimal, said reservoir (50) fills partially or totally with working gas (5) when said first hydraulic expansion valve variable volume (44) is maximal, the variation in the volume of the working gas (5) contained in the first expansion valve gas and liquid reservoir (50) defining, on the one hand, a pneumatic expansion valve variable volume (136) and being, on the other hand, approximately equal to the variation in the volume of the working liquid (13) contained in the first hydraulic expansion valve variable volume (44);At least one second regulator gas and liquid reservoir (55) which is connected to the second hydraulic regulator variable volume (46) by a communicating conduit (15), such that said reservoir (55) fills mostly or totally with working liquid (13) when the second hydraulic regulator variable volume (46) is minimal, said reservoir (29) fills partially or totally with working gas (5) when said second hydraulic regulator variable volume (46) is maximal, the variation in the volume of the working gas (5) contained in the second regulator gas and liquid reservoir (55) defining, on the one hand, a pneumatic regulator variable volume (136) and being, on the other hand, approximately equal to the variation in the volume of the working liquid (13) contained in the second hydraulic regulator variable volume (46); The first compressor heat exchange and accumulation means (16) which are housed in the first compressor gas and liquid reservoir (14) and second compressor heat exchange and accumulation means (59) which are housed in the second compressor gas and liquid reservoir (29), said means (16, 59) each being able to mainly take heat from the working gas (5) contained in the reservoir (14, 29) in which they are housed, and temporarily store said heat, before transferring the latter to the working liquid (13) also contained in said reservoir (14, 29); First means of heat exchange and accumulation of regulator (139) which are housed in the first regulator gas and liquid reservoir (50) and second means of heat exchange and accumulation of regulator (70) which are housed in the second regulator gas and liquid reservoir (55), said means (139, 70) each being able to mainly take heat from the working liquid (13) which is contained in the reservoir (50, 55) in which they are housed, and temporarily store said heat, this before releasing the latter to the working gas (5) which is also contained in said reservoirs (50, 55);First heat export means (17) housed inside and / or outside the first compressor gas and liquid tank (14) and second heat export means (73) housed inside and / or outside the second compressor gas and liquid tank (29), said means (17, 73) taking heat directly or indirectly respectively from the first compressor heat exchange and accumulation means (16) and from the second compressor heat exchange and accumulation means (59) on the one hand, and / or from the working liquid (13) and / or from the working gas (5) which are contained in whole or in part in said tanks (14, 29) on the other hand, said heat being subsequently transferred to heating means (18) external to said tanks (14, 29); First heat import means (138) housed inside and / or outside the first gas and liquid expansion valve reservoir (50) and second import means of heat (74) housed inside and / or outside the second gas and liquid expansion tank (55), said means (138, 74) directly or indirectly supplying heat respectively to the first heat exchange and accumulation means of expansion tank (139) and to the second heat exchange and accumulation means of expansion tank (70) on the one hand, and / or to the working liquid (13) and / or to the working gas (5) which are contained in whole or in part in said tanks (50, 55) on the other hand, said heat having been previously taken from cooling means (19) external to said tanks (50, 55); Compressor filling means (20) that permit or prohibit the passage of working gas (5) from a compressor inlet plenum (21) to the first compressor gas and liquid reservoir (14) via at least one inlet port (6) while other compressor filling means (20) permit or prohibit the passage of working gas (5) from said plenum (21) or from another compressor inlet plenum (21) to the second compressor gas and liquid reservoir (29) via at least one other inlet port (6); Compressor draining means (22) that permit or prohibit the passage of working gas (5) from the first compressor gas and liquid reservoir (14) to a compressor discharge plenum (62) via at least one outlet port (7) while other compressor draining means (22) permit or prohibit the passage of working gas (5) from the second compressor gas and liquid reservoir (29) to said plenum (62) or to another compressor discharge plenum (62) via at least one other outlet port (7); Regulator filling means (140) that permit or prevent the passage of working gas (5) from a regulator inlet plenum (142) to the first regulator gas and liquid reservoir (50) via at least one inlet port (6), while other means regulator filling (140) permit or prohibit the passage of working gas (5) from said plenum (142) or from another regulator inlet plenum (142) to the second regulator gas and liquid reservoir (55) via at least one other inlet port (6); Regulator draining means (141) that permit or prohibit the passage of working gas (5) from the first regulator gas and liquid reservoir (50) to a regulator discharge plenum (143) via at least one outlet port (7) while other regulator draining means (141) permit or prohibit the passage of working gas (5) from the second regulator gas and liquid reservoir (55) to said plenum (143) or to another regulator discharge plenum (143) via at least one other outlet port (7); A compressor connecting rod (11) which is integral with the double-acting hydraulic piston of compressors (10), which passes in a sealed manner through at least one of the sealed terminations of compressor cylinder (135) and which is approximately parallel to the longitudinal axis of said piston (10) and of the blind liquid cylinder of compressors (8); A regulator connecting rod (75) which is integral with the double-acting hydraulic regulator piston (39), which passes through at least one of the sealed regulator cylinder terminations (78), and which is approximately parallel to the longitudinal axis of said piston (39) and the blind regulator liquid cylinder (30); Compressor piston guiding means (23) that maintain the double-acting hydraulic compressor piston (10) and the compressor connecting rod (11) parallel to the blind liquid compressor cylinder (8), regardless of the position of said piston (10) in said cylinder (8); Piston guide means for pressure regulators (77) that retain the double-acting hydraulic pressure regulator piston (39) and the pressure regulator connecting rod (75) parallel to the blind liquid cylinder of expansion valves (30), regardless of the position of said piston (39) in said cylinder (30); • Means of actuating connecting rods (144) through which at least one drive motor (27) imparts, on the one hand, to the connecting rod of compressors (11) a reciprocating longitudinal translational movement parallel to the axis of the blind liquid cylinder of compressors (8), and on the other hand, to the connecting rod of expansion valves (75) a reciprocating longitudinal translational movement parallel to the axis of the blind liquid cylinder of expansion valves (30);• Means of storing mechanical energy (28) which are directly or indirectly connected to the means of actuating connecting rods (144) or which are directly or indirectly connected to the connecting rod of expansion valves (75) or to the connecting rod of compressors (11), said storage means (28) being able to alternately take and give mechanical energy to said actuating means (144) or to said rods (75, 11).;

2. Mechanical-liquid piston heat pump according to claim 1, characterized in that the means for actuating connecting rods (144) consist of a crankshaft (24) which can rotate in at least one shaft bearing (25) which is directly or indirectly integral with the static frame (40), said crankshaft (24) having at least one crank (26) around which is articulated a connecting rod head (145) of an actuating connecting rod (165), the latter also having a connecting rod foot (146) which is articulated as appropriate either with the connecting rod of compressors (11), or with the connecting rod of expansion valves (75).

3. A mechanical-liquid piston heat pump according to claim 2, characterized in that the crankshaft (24) has two cranks (26), the first of said cranks (26) being connected by a first connecting rod (165) to the compressor connecting rod (11), while the second of said cranks 67 (26) is connected by a second actuating rod (165) to the connecting rod of the regulators (75).

4. Mechanical-liquid piston heat pump according to claim 2, characterized in that the connecting rod foot (146) is articulated, as the case may be, with the connecting rod of compressors (11) or with the connecting rod of expansion valves (75) by means of a connecting hook (147) which is integral with said rod (11, 75).

5. Mechanical-liquid piston heat pump according to claim 4, characterized in that the connecting arm (147) comprises an arm yoke (148) which is traversed by an arm shaft (155) which is perpendicular, as the case may be, to the connecting rod of compressors (11) or to the connecting rod of expansion valves (75), and around which are articulated on the one hand, a connecting rod foot bearing (149) which comprises the connecting rod foot (146), and at least one arm roller (150) which rolls on at least one arm bearing raceway (41) which is parallel, as the case may be, to the blind liquid cylinder of compressors (8) or to the blind liquid cylinder of expansion valves (30), and which is directly or indirectly integral with said cylinder (8, 30).

6. Mechanical-liquid piston heat pump according to claim 1, characterized in that the first compressor heat exchange and accumulation means (16) and / or the second compressor heat exchange and accumulation means (59) and / or the first expansion valve heat exchange and accumulation means (139) and / or the second expansion valve heat exchange and accumulation means (70) are made of a porous medium (32) which has porosities (33) into which working liquid (13) and working gas (5) alternately enter and exit.

7. A mechanical-liquid piston heat pump according to claim 1, characterized in that the first heat export means (17) consist of a circulating portion of the working fluid (13) which exits the first hydraulic variable volume of the compressor (12) and / or the first gas and fluid reservoir of the compressor (14) via a liquid outlet conduit (34), said circulating portion then returning to said first volume (12) and / or to said first reservoir (14) via a liquid inlet conduit (35), this after to have directly or indirectly transferred heat to the heating means (18)

8. Mechanical-liquid piston heat pump according to claim 1, characterized in that the second heat export means (73) consist of a circulating portion of the working fluid (13) which exits the second hydraulic variable volume of the compressor (134) and / or the second gas and fluid tank of the compressor (29) via a liquid outlet conduit (34), said circulating portion then returning to said second volume (134) and / or to said second tank (29) via a liquid inlet conduit (35), this after having directly or indirectly transferred heat to the heating means (18).

9. Mechanical-liquid piston heat pump according to any one of claims 7 and 8, characterized in that the circulating part of the working fluid (13) transfers heat to the heating means (18) via at least one secondary heating heat exchanger (153).

10. Mechanical-liquid piston heat pump according to claim 1, characterized in that the first heat import means (138) consist of a circulating portion of the working fluid (13) which exits the first hydraulic variable volume of the expansion valve (44) and / or the first gas and liquid expansion valve reservoir (50) via a liquid outlet conduit (34) to return to said first volume (44) and / or to said first reservoir (50) via a liquid inlet conduit (35), this after having directly or indirectly taken heat from the cooling means (19).

11. Mechanical-liquid piston heat pump according to claim 1, characterized in that the second heat import means (74) consist of a circulating portion of the working liquid (13) which exits the second hydraulic variable expansion volume (46) and / or the second expansion gas and liquid reservoir (55) via a liquid outlet conduit (34) to return to said second volume (46) and / or to said second reservoir (55) via a liquid inlet conduit (35), this after having directly or indirectly taken heat from the cooling means (19).

12. A mechanical-liquid piston heat pump according to any one of claims 10 and 11, characterized in that the circulating portion of the working fluid (13) absorbs heat by means cooling (19) via at least one secondary cooling heat exchanger (154).

13. Mechanical-liquid piston heat pump according to claim 1, characterized in that the first heat export means (17) consist of at least one heat exchanger duct (36) housed in the first compressor gas and liquid tank (14) and in which circulates a heat transfer fluid (37) which exports heat taken from the first compressor heat exchange and storage means (16) on the one hand, and / or from the working fluid (13) and / or from the working gas (5) contained in the first compressor gas and liquid tank (14) on the other hand, to the heating means (18), via heat transport ducts (38).

14. Mechanical-liquid piston heat pump according to claim 1, characterized in that the second heat export means (73) consist of at least one heat exchanger duct (36) housed in the second compressor gas and liquid tank (29) and in which circulates a heat transfer fluid (37) which exports heat taken from the second compressor heat exchange and storage means (59) on the one hand, and / or from the working fluid (13) and / or from the working gas (5) contained in the second compressor gas and liquid tank (29) on the other hand, to the heating means (18), via heat transport ducts (38).

15. Mechanical-liquid piston heat pump according to claim 1, characterized in that the first heat import means (138) consist of at least one heat exchanger duct (36) housed in the first expansion valve gas and liquid tank (50) and in which circulates a heat transfer fluid (37) which imports heat from the cooling means (19) to the first expansion valve heat exchange and storage means (139) on the one hand, and / or the working fluid (13) and / or the working gas (5) contained in the first expansion valve gas and liquid tank (50) on the other hand, via heat transport ducts (38).

16. A mechanical-liquid piston heat pump according to claim 1, characterized in that the second heat import means (74) consist of at least one heat exchanger duct (36) housed in the second expansion valve gas and liquid reservoir (55) and through which circulates a heat transfer fluid (37) which imports of heat from the cooling means (19) to the second means of heat exchange and heat accumulation of the expansion valve (70) on the one hand, and / or the working liquid (13) and / or the working gas (5) contained in the second expansion valve gas and liquid tank (55) on the other hand, via heat transport ducts (38).

17. Mechanical-liquid piston heat pump according to claim 1, characterized in that the first compressor heat exchange and accumulation means (16) and / or the second compressor heat exchange and accumulation means (59) consist of at least one liquid spray nozzle (71) supplied by a liquid spray pump (72), said nozzle (71) being able, as appropriate, to atomize working liquid (13) into fine droplets in the internal volume of the first compressor gas and liquid tank (14) or in the internal volume of the second compressor gas and liquid tank (29).

18. Mechanical-liquid piston heat pump according to claim 1, characterized in that the first means for heat exchange and accumulation of the expansion valve (139) and / or the second means for heat exchange and accumulation of the expansion valve (70) consist of at least one liquid spray nozzle (71) supplied by a liquid spray pump (72), said nozzle (71) being able, as appropriate, to atomize working liquid (13) into fine droplets in the internal volume of the first expansion valve gas and liquid reservoir (50) or in the internal volume of the second expansion valve gas and liquid reservoir (55).

19. A mechanical-liquid piston heat pump according to claim 1, characterized in that the first compressor heat exchange and accumulation means (16) and / or the second compressor heat exchange and accumulation means (59) consist of a rotary liquid atomizer (158) comprising a rotary atomizing cylinder (159) perforated with radial atomizing orifices (160), an atomizer motor (161) driving said cylinder (159) in rotation sufficiently rapid so that the latter draws working liquid (13) into its axial end by centrifugal force and / or by means of a pumping turbine (162), and radially discharges said liquid (13) in the form of fine droplets into the internal volume of the first gas reservoir and

20.

21.

22. compressor fluid (14) if said atomizer (158) is housed in said first tank (14), or in the internal volume of the second gas and compressor fluid tank (29) if said atomizer (158) is housed in said second tank (29), via the radial atomizing ports (160). Mechanical-liquid piston heat pump according to claim 1, characterized in that the first means for heat exchange and accumulation of the expansion valve (139) and / or the second means for heat exchange and accumulation of the expansion valve (70) consist of a rotary liquid atomizer (158) which comprises a rotary atomizing cylinder (159) pierced with radial atomizing orifices (160), an atomizer motor (161) driving said cylinder (159) in rotation sufficiently rapid so that the latter draws working liquid (13) into its axial end by centrifugal force and / or by means of a pumping turbine (162), and radially discharges said liquid (13) in the form of fine droplets into the internal volume of the first gas and liquid expansion valve reservoir (50) if said atomizer (158) is housed in said first reservoir (50),or in the internal volume of the second gas and liquid regulator reservoir (55) if said atomizer (158) is housed in said second reservoir (55), via the radial atomization ports (160). Mechanical-liquid piston heat pump according to claim 1, characterized in that the compressor piston guiding means (23) and / or the expansion piston guiding means (77) are made up of at least one sliding pivot joint (47) formed on the one hand, between an external cylindrical surface (48) which is present in the compressor connecting rod (11) and the expansion connecting rod (75), and on the other hand, a guide orifice (49) provided in the sealed termination(s) of the compressor cylinder (135) through which the compressor connecting rod (11) passes in the case of the latter (11), or a guide orifice (49) provided in the sealed termination(s) of the expansion cylinder (78) through which the expansion connecting rod (75) passes in the case of said expansion connecting rod (75). A mechanical-liquid piston heat pump according to claim 21, characterized in that the sliding pivot joint (47) comprises a hinged connecting tube (9) which has at one of its ends a sealed ball joint of rod (79) which articulates as appropriate around the connecting rod of compressors (11) or around the connecting rod of expansion valves (75), said articulated tube (9) having at its other end a sealed ball joint of termination (80) which articulates as appropriate with the sealed termination of compressor cylinder (135) or with the corresponding sealed termination of expansion cylinder (78).

23. Mechanical-liquid piston heat pump according to claim 1, characterized in that the piston guiding means of compressors (23) and / or the piston guiding means of expansion valves (77) are made up of a guide skirt (57) arranged on the periphery of the double-acting hydraulic piston of compressors (10) or on the periphery of the double-acting hydraulic piston of expansion valves (39), said skirt (57) being able to translate with little clearance in the blind liquid cylinder of compressors (8) or in the corresponding blind liquid cylinder of expansion valves (30).

24. Mechanical-liquid piston heat pump according to claim 1, characterized in that the compressor filling means (20) and / or the compressor draining means (22) consist of at least one compressor valve (52) and / or at least one piloted compressor valve (53).

25. Mechanical-liquid piston heat pump according to claim 1, characterized in that the expansion valve filling means (140) and / or the expansion valve emptying means (141) consist of at least one pilot-operated expansion valve (54).

26. A mechanical-liquid piston heat pump according to claim 1, characterized in that the compressor discharge plenum (62) is connected to the expansion valve inlet plenum (142) by a high-pressure gas line (56) such that the working gas (5) exiting the pneumatically variable compressor volumes (2) via said compressor discharge plenum (62) is introduced into the pneumatically variable expansion volumes (136) via said expansion valve inlet plenum (142), while the expansion valve discharge plenum (143) is connected to the compressor inlet plenum (21) by a low-pressure gas line (61) such that the working gas (5) exiting the pneumatically variable expansion volumes (136) via said expansion valve discharge plenum (143) is introduced into the pneumatic variable volumes of compressor (2) via said compressor inlet plenum (21).

27. ​​Mechanical-liquid piston heat pump according to claim 26, characterized in that the high-pressure gas conduit (56) communicates with at least one high-pressure gas reservoir (58).

28. Mechanical-liquid piston heat pump according to claim 26, characterized in that the low-pressure gas conduit (61) communicates with at least one low-pressure gas reservoir (60).

29. Mechanical-liquid piston heat pump according to claim 26, characterized in that the working gas (5) which flows in the high-pressure gas duct (56) transfers its heat to the working gas (5) which flows in the low-pressure gas duct (61) via a regeneration heat exchanger (152).

30. Mechanical-liquid piston heat pump according to claim 1, characterized in that the compressor inlet plenum (21) and the compressor outlet plenum (62) are part of a compressor cylinder head (110) which covers the upper part of the first compressor gas and liquid tank (14) and the second compressor gas and liquid tank (29), the latter (14, 29) being themselves positioned mainly above the blind compressor liquid cylinder (8), so that, under the effect of Earth's gravity, the working gas (5) is always first to exit said tanks (14, 29) via said outlet plenum (62) while the working liquid (13) is always first to enter said tanks (14, 29) via said inlet plenum (21).

31. A mechanical-liquid piston heat pump according to claim 1, characterized in that the expansion valve inlet plenum (142) and the expansion valve outlet plenum (143) are part of an expansion valve cylinder head (111) which covers the upper part of the first expansion valve gas and liquid reservoir (50) and the second expansion valve gas and liquid reservoir (55), the latter (50, 55) being themselves positioned primarily above the expansion valve blind liquid cylinder (30), so that, under the effect of Earth's gravity, the working gas (5) is always the first to exit said reservoirs (50, 55) via said outlet plenum (143), however that the working fluid (13) is always the first to enter said reservoirs (50, 55) via said inlet plenum (142).

32. Mechanical-liquid piston heat pump according to claim 2, characterized in that the mechanical energy storage means (28) consist of a flywheel (66) made rotationally fixed to the crankshaft (24) by a transmission multiplier (156).

33. Mechanical-liquid piston heat pump according to claim 2, characterized in that the crankshaft (24) comprises a toothed ring (67) which the drive motor (27) drives in rotation by means of at least one ring drive pinion (68) whose pitch diameter is smaller than that of said ring (67), the latter (67) and said pinion (68) forming a multiplication gear system (69).

34. Mechanical-liquid piston heat pump according to claim 1, characterized in that the outlet ports (7) which open into the compressor discharge plenum (62) or those (7) which open into the expansion valve discharge plenum (143) each form an overflow tank (113) in which working fluid (13) can be stored, said tank (113) being arranged such that when the compressor draining means (22) or, as the case may be, the expansion valve draining means (141), allow the passage of working gas (5) via said ports (7), said gas (5) having to pass through said tank (113) before opening, as the case may be, into the compressor discharge plenum (62) or into the expansion valve discharge plenum (143).

35. Mechanical-liquid piston heat pump according to claim 34, characterized in that the overflow tanks (113) formed by the outlet ports (7) of the first compressor gas and liquid tank (14) and those (7) of the second compressor gas and liquid tank (29) open into the same compressor discharge plenum (62) but are separated by a leveling dike (114) which tends to equalize the working liquid levels (13) in said tanks (113) when the compressor draining means (22) associated with said tanks (14, 29) prevent the passage of working gas (5).

36. A mechanical-liquid piston heat pump according to claim 34, characterized in that the overflow tanks (113) formed by the outlet ports (7) of the first regulator gas and liquid tank (50) and those (7) of the second regulator gas and liquid tank (55) open into the same regulator discharge plenum (143) but are separated by a leveling dike (114) which tends to equalize the working liquid levels (13) in said tanks (113) when the regulator draining means (141) associated with said tanks (50, 55) prohibit the passage of working gas (5).

37. Mechanical-liquid piston heat pump according to claim 1, characterized in that a working liquid level equalization valve (115) can connect the first compressor gas and liquid tank (14) or the second compressor gas and liquid tank (29) with the first expansion valve gas and liquid tank (50) or the second expansion valve gas and liquid tank (55).

38. Liquid-mechanical piston heat pump according to claim 1, characterized in that a defrost heat reservoir (116) is heated by the first heat export means (17) and / or the second heat export means (73) and can transfer its heat to the cooling means (19).

39. Mechanical-liquid piston heat pump according to claim 15, 16 and 38, characterized in that the defrosting heat reservoir (116) is formed of a heat transfer fluid reservoir (123) connected in bypass of the heat transport duct (38) which transports the heat transfer fluid (37) to the cooling means (19), said fluid (37) being able either to pass through said reservoir (123) before reaching the cooling means (19) to heat the latter, or to bypass said reservoir (123) to reach said means (19) directly.

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