Slow compression-expansion device with mechanical-liquid piston

Abstract

A slow expansion compressor (1) of the mechanical liquid piston type comprises a liquid cylinder (8) which pivots about a tilt axis (9) and in which a hydraulic piston (10) is translated, which hydraulic piston is firmly fixed to a connecting rod (11) of a crank (26) connected to a crankshaft (24), the axis of rotation of which is parallel to the tilt axis (9), and a piston guide member (23) maintaining the connecting rod (11) and the hydraulic piston (10) always parallel to the hydraulic cylinder (8), both forming a variable hydraulic volume (12) filled with the working liquid (13), communicating with a gas and liquid reservoir (14) in which the heat exchange and accumulation member (16) is housed, the reservoir (14) and the liquid (13) form a variable pneumatic volume (2) in which the working gas (5) is compressed or expanded.

Description

[0001] This invention relates to a mechanical liquid piston type slow expansion compressor.

[0002] In many areas of human activity, whether in industry, agriculture, or transportation, or in residential or commercial settings, various compressors are used to compress gases, and in particular, heat pumps are used to generate heat or cold.

[0003] Whether it involves producing the compressed air necessary for a machine or method, or ensuring the operation of a heat pump intended for heating or air conditioning, the efficiency of the compressor is a decisive factor that has a significant impact on energy consumption.

[0004] In most applications, the heat generated during gas compression constitutes an irreversible energy loss. For such applications, the ideal compressor would be an isothermal compressor, i.e., one that releases the heat generated by gas compression as it is produced, in order to minimize the work required for the compression.

[0005] However, in practice, it is impossible to produce a completely isothermal compressor because a temperature difference must exist between the gas and the heat-absorbing well in order for the heat from the compression of the gas to be transferred instantly at the moment of generation.

[0006] However, isothermal compression can be achieved by using a heat-exporting component positioned at the core of the gas, which exposes the gas to a large heat exchange surface as much as possible, allowing the gas to move in a turbulent manner that facilitates convective heat exchange. At the same time, this constrains any heat dissipation through radiation in a closed chamber and by allowing time for heat exchange.

[0007] However, quasi-isothermal compression is insufficient to guarantee high compressor efficiency because non-thermodynamic energy loss is unavoidable and must be minimized.

[0008] Of the non-thermodynamic energy losses, mechanical losses are manifested as friction of the compressor itself or friction associated with its accessories. Pressure losses, also known as "load losses," occur at the compressor vanes or at the inlet and outlet valves, or at the conduits connecting the compressor to the point of compressed gas consumption, or may also occur at sealing losses inside or outside the compressor.

[0009] Within the scope of ecological transformation, heat pumps that integrate gas compressors play an important role because they can heat and air-condition buildings at a lower energy cost by extracting renewable heat into the environment.

[0010] With global warming occurring worldwide and the evolution of lifestyles, building air conditioning alone already consumes more than 10 percent of the world’s electricity production, and this share is expected to grow significantly in the coming years, both in proportion and in volume, to the point that heat pump efficiency represents a major energy challenge.

[0011] The same applies to building heating, which itself consumes more than 20 percent of the world’s primary energy and is expected to rely on cryogenic heat pumps, the most efficient type of heat pump, on a large scale in the coming decades.

[0012] The principle of heat pumps currently used worldwide is mainly based on the change of state of the refrigerant fluid (from vapor to liquid, or vice versa), with the saturated vapor pressure of the refrigerant fluid adapted to the target heating or cooling temperature range and the pressure that the equipment can support.

[0013] State or phase-changing refrigeration cycles have the advantage of high heat or cold power density because they utilize the latent heat of evaporation or condensation of the refrigerant fluid by modulating the pressure and temperature of the fluid to cause the fluid to evaporate or condense.

[0014] In current technology, and considering economic, technical, physical limitations as well as limitations in the production of heat pumps, the state-changing refrigeration cycle is still far from the most efficient.

[0015] However, not all refrigeration cycles rely on changes in the state of a specially formulated refrigerant fluid.

[0016] For example, the Brayton-Joule cycle (also known as the Bell-Coleman cycle) provides compression and isentropic expansion of a gas without a change of state, wherein, after compression, the gas undergoes heat transfer to a cooler environment at constant pressure, and wherein, after expansion, the gas also undergoes thermal puncture at constant pressure into a chamber to be cooled.

[0017] However, the actual efficiency of the Bell-Coleman cycle remains low, with a coefficient of performance (COP) of only slightly higher than one in practice and usually less than one. In contrast, state-change and refrigerant fluid heat pumps have a COP that can reach its peak, i.e., four or even five. This means that for one unit of energy input, up to four or five units of energy in the form of heat or cold can be collected.

[0018] Due to its low actual energy efficiency, the Bell-Coleman cycle is mainly used only when compressed air is naturally available, which may be the case on airplanes and some trains.

[0019] In contrast to Bell-Coleman cycle heat pumps, refrigerant fluid and state-changing heat pumps are widely used for heating or air conditioning buildings due to their high efficiency.

[0020] However, the efficiency of refrigerant fluid heat pumps is still far below the ideal Carnot efficiency. By using the temperature difference that is usually reserved for measurement, the coefficient of performance for the ideal Carnot efficiency would be greater than 20, while the best heat pumps currently on the market achieve a coefficient of performance of 5.

[0021] However, the ideal Carnot efficiency is only an indicator of the maximum efficiency that can be achieved in theory, because it does not take into account either the temperature difference necessary for heat exchange to occur, nor the mechanical and actual stresses involved in producing a heat pump.

[0022] However, given the scarcity of energy and the climate and ecological challenges associated with it, maximizing the coefficient of performance (COP) of heat pumps used for heating, air conditioning, or cooling, and bringing them as close as possible to the ideal Carnot efficiency, would be a significant advantage.

[0023] With a suitable and efficient compression and expansion machine, it may actually approach the ideal efficiency of the Carnot cycle.

[0024] To achieve this goal, the machine's compressor must compress the gas in two consecutive steps.

[0025] The first step involves adiabatic compression, which occurs until the temperature of the gas is high enough that it can transfer heat to, for example, a heating circuit in a building. The second step is isothermal compression, during which the temperature reached by the gas at the end of the adiabatic compression is maintained during the remainder of the gas compression by gradually transferring the heat generated by the isothermal compression to the heating circuit, and this continues until the gas is depressurized outside the compressor.

[0026] Then, the expander of the machine must also expand the pre-compressed gas in two consecutive steps according to the reverse process described above.

[0027] The first step involves adiabatic expansion, which occurs until the temperature of the gas is low enough that the gas can extract heat from the environment, for example, outside the building. The second step is isothermal expansion, during which the temperature reached by the gas at the end of the adiabatic expansion is maintained during the remainder of the expansion by gradually extracting the heat necessary to maintain that temperature from the environment during the remainder of the isothermal expansion, and this continues until the gas is depressurized outside the compressor.

[0028] One of the advantages of this type of heat pump is that it no longer resorts to polluting, toxic, or flammable refrigerant fluids, some of which damage the ozone layer or contribute to a strong greenhouse effect.

[0029] The importance of refrigerant fluids no longer outweighs the proposed regulations that would ban refrigerant fluids with a global warming potential greater than or equal to 150 times that of carbon dioxide starting in 2030.

[0030] These regulations will reduce the amount of refrigerant fluid that can be used in conventional heat pumps and will significantly impact the technology of such pumps, even increasing their cost.

[0031] The most likely alternative to the refrigerant fluid currently used in conventional heat pumps is carbon dioxide, which is a pollution-free gas with a low specific global warming potential, but has the major disadvantage of a high operating pressure of over one hundred atmospheres, making it more difficult to guarantee the sealing and safety of the equipment.

[0032] Therefore, it should be understood that it is of great importance to reproduce Sadie Carnot's ideal heat pump cycle as faithfully as possible by producing quasi-isothermal compressors and volumetric expanders that use fluids that remain in a gaseous state throughout the cycle.

[0033] This approach can only be achieved by applying a stable setpoint temperature to the gas during compression or isothermal expansion, which can be accomplished using a medium that stores heat directly in the compression or expansion chamber, the medium being associated with a component that removes the heat during the compression phase or introduces the heat during the expansion phase.

[0034] Several designs describe near-isothermal compressors or expanders having components for storing, introducing, or removing heat.

[0035] For example, the quasi-isothermal machine described in patent GB2534244 is such a machine, which includes a downwardly oriented piston with a heat absorption and return structure, the piston compressing gas in a variable volume with a constant fluid volume at the bottom of the variable volume.

[0036] According to the invention of patent GB2534244, the piston compresses or expands the gas while forcing the gas into contact with a heat absorption and return structure for cooling or heating. The structure can be made of metal plates, which are outside the liquid that exchanges heat with the gas, but exchange heat with the liquid when they are immersed in the liquid.

[0037] According to the invention in patent GB2534244, the liquid remains nearly stationary, which is the opposite of a liquid piston compressor, in which the liquid is actually moving. This means that the liquid will not experience a deceleration that is too far from the Earth's gravity, thus avoiding cavitation and fluctuations in the liquid.

[0038] Conversely, the invention of patent GB2534244 thus makes it possible to manufacture compressors or rapidly rotating expanders without causing liquid movement, which has the advantage of giving the compressor or expander a high volumetric power density.

[0039] It should be noted that the specific configuration of patent GB2534244 proposes a relatively conventional rod and crank system to actuate the piston that carries the heat absorption and return structure.

[0040] Another method is to move the liquid by means of a piston that translates within the cylinder, as provided in patent CN111734604, which, in contrast to patent GB2534244, immerses the static radiator in the liquid.

[0041] Numerous published documents, including patent CN111734605, also mention liquid pistons, which alternatively force gas and liquid through porous media or thermal accumulation and return systems.

[0042] This technical approach is specifically employed in various research projects dedicated to energy storage systems in the form of compressed air, for example, with the aim of accumulating renewable energy generated by offshore wind turbines.

[0043] It can be concluded from most of these devices that, regardless of their nature, the efficiency of compression or expansion is highly dependent on the total heat exchange surface between the gas, liquid, and heat absorption and return structures, and on the time allowed for the exchange to occur.

[0044] Therefore, to facilitate the exchange, it is preferable to produce a slow-rotating compressor or expander, at the cost of lower volumetric power.

[0045] Besides allowing time for heat exchange to occur, the advantage of slowly rotating compressors or expanders is that they allow time for gas transfer to occur, thereby limiting pressure losses at the inlet and outlet ports of the compressor and expander.

[0046] In fact, if the slow-rotating compressor or expander rotates slowly, their actual thermodynamic pressure-volume diagram will be close to the ideal theoretical diagram because there is less deformation caused by gas transfer, and the actual efficiency of the heat pump integrating the compressor and expander will be closer to the maximum theoretical efficiency achievable according to the ideal Carnot cycle.

[0047] In fact, the inertial forces that reduce the performance of the controlled vanes and valves responsible for delivering gas to or from the compressor or expander evolve more or less with the square of the rotational speed of the compressor or expander.

[0048] This results in a delay in the opening and / or closing of the vanes and valves, which affects the efficiency of the thermodynamic cycle.

[0049] Therefore, from the above, a slow-rotating single-phase heat pump that compresses and expands a gas according to the Carnot cycle will initially occupy a larger volume than its conventional equivalent, whose refrigerant fluid changes sequentially from a gaseous state to a liquid state, or vice versa, and whose compressor operates at a high speed.

[0050] The problem with slow-rotating compressors and expanders is that, at the same power, the mechanical parts that make them up are subjected to greater forces than their faster-rotating counterparts, and the large size of these parts, resulting from these forces, leads to high energy loss due to friction.

[0051] In addition to the large size of the parts, the disadvantage of the slow rotation of the compressor or expander is that it is not conducive to establishing a hydrodynamic lubrication system between the parts, for example at the friction interface of the piston in the cylinder, or at the pivot connection between the piston and the rod, between the rod and the crankshaft, and between the crankshaft and the housing.

[0052] Therefore, it would be highly advantageous to realize a liquid piston coupled with heat exchange, storage, return, import and export components by means of a very mechanically efficient slow machine that allows sufficient time for heat exchange to maximize its efficiency on the one hand and sufficient time for gas transfer to minimize its energy loss on the other.

[0053] This configuration will enable the production of high-energy-performance heat pumps with efficiencies closer to those of the ideal Carnot cycle, superior to their conventional counterparts that change the refrigerant fluid under different operating conditions, and requiring only, for example, atmospheric air and water, for operation.

[0054] For example, the configuration could potentially achieve a coefficient of performance (COP) of approximately seven, while under the same measurement conditions and in the same environment, the COP of the best refrigerant fluid heat pump on the market would be approximately five.

[0055] However, as described above, to achieve this efficiency difference, quasi-isothermal compression and expansion must be produced, which is achieved by maximizing heat exchange during said compression and said expansion, minimizing losses caused by transmission, losses caused by internal or external gas leakage, and minimizing losses caused by friction.

[0056] For example, the coefficient of performance of a Carnot cycle single-phase heat pump is necessarily very sensitive to the energy efficiency of its mechanical drive due to the necessity of its compression ratio to a larger amount of gas corresponding to its refrigerant fluid state change. If the efficiency is insufficient, the efficiency of the Carnot cycle single-phase heat pump will be lower than that of its counterpart.

[0057] In fact, since a Carnot cycle single-phase heat pump must compress a larger amount of gas than its refrigerant fluid counterpart undergoing a state change, the coefficient of performance of the single-phase heat pump is highly dependent on the energy efficiency of its gas compression and expansion mechanical transmission.

[0058] If the efficiency is insufficient, the coefficient of performance (COP) of the single-phase heat pump will be lower than that of its refrigerant fluid counterpart.

[0059] For example, when the target performance coefficient is greater than five, the Carnot cycle single-phase heat pump is more sensitive to the mechanical efficiency of compression and expansion.

[0060] For example, a Carnot cycle single-phase heat pump that achieves 10 kW of thermal power with a performance coefficient of 5 requires an external energy input of 2 kW in the form of mechanical work.

[0061] If the mechanical efficiency of the single-phase heat pump is generally low and results in a mechanical loss of one kilowatt, the pump's coefficient of performance drops from five to three point three, and the pump owner's energy bill increases by fifty percent.

[0062] In this case, the single-phase heat pump loses all or almost all of its advantages relative to its conventional equivalents of refrigerant fluid with a change in state.

[0063] This is why the mechanical liquid reciprocating slow-expansion compressor according to the invention provides an innovative configuration with very high mechanical and volumetric efficiency, which, combined with efficient heat exchange and flow, gives, in particular, a Carnot cycle single-phase heat pump a coefficient of performance significantly higher than that of its conventional equivalents of state-changing refrigerant fluids.

[0064] Therefore, mechanical liquid reciprocating slow expansion compressors are primarily provided for producing, on the one hand, high-energy-efficiency compressors and / or expanders that can be used in any field of activity, and on the other hand, high-performance coefficient heat pumps.

[0065] The mechanical-liquid piston-type slow-expansion compressor according to the present invention specifically produces a heat pump such that:

[0066] • The coefficient of performance of this heat pump is greater than that of a conventional heat pump that changes the refrigerant fluid, therefore, under the same conditions, the pump according to the invention reduces the energy required to generate heat or cold.

[0067] • The thermodynamic efficiency of this heat pump is so close to the ideal thermodynamic efficiency of the Carnot cycle that it is virtually impossible to surpass that it would be almost impossible to replace the heat pump with another design simply by further improving the efficiency.

[0068] • This heat pump does not resort to any refrigerant fluid that is harmful to health or the environment, and the pump is capable of operating, for example, with atmospheric air or nitrogen and avoids any regulatory or safety restrictions related to the disposal, storage or recovery of refrigerant fluids;

[0069] • Because this heat pump does not rely on any refrigerant fluid at all, the pump has a very wide operating temperature range and can operate in heating or air conditioning mode in any region of the world without compromising its efficiency;

[0070] • This heat pump has a simple design, so much so that it can be manufactured in workshops of average technical level in almost all countries of the world, specifically by assembling low-cost components that can be easily produced or are widely available on the market.

[0071] • The simple mechanical design of this heat pump makes it possible to maintain it at a low cost without requiring advanced technical skills;

[0072] • This heat pump enables any qualified plumber / heating engineer to easily and achievably produce heating and air conditioning networks that can be readily integrated into buildings and their environments without requiring approvals or certifications related to the disposal of gases that are hazardous to health and the environment.

[0073] • The robust mechanism of this heat pump allows it to last for decades or even over a century with the replacement of small parts, without any degradation in the pump's operation and efficiency. When analyzing the pump's entire lifespan (including manufacturing and recycling), this lifespan constitutes an additional environmental advantage compared to conventional refrigerant fluid heat pumps.

[0074] • This heat pump is silent and can be integrated into buildings with minimal noise pollution.

[0075] • The arrangement of this heat pump enables the exposure of large heat exchange surfaces to the environment at a lower cost by employing electric fans with low rotation speed, low energy consumption, and low noise emission.

[0076] • The manufacture of this heat pump does not require rare or strategic materials, nor does it require high-tech proprietary technology and knowledge.

[0077] It should be understood that the mechanical liquid piston slow expansion compressor according to the invention relates not only to a heat pump but also to a compressor and to a gas expander, and to any other application that is similar in design and principle to which the specific features and functions of the expansion compressor according to the invention can be advantageously utilized.

[0078] Other features of the invention have been described in the specification and in the minor claims that are directly or indirectly dependent on the main claims.

[0079] A mechanical-liquid reciprocating slow-expansion compressor defines a variable pneumatic volume, which forms a compressor or expander, through which working gas can enter or exit the volume via an inlet port. The mechanical-liquid reciprocating slow-expansion compressor includes:

[0080] • A liquid cylinder that can pivot directly or indirectly about an inclined axis perpendicular to the cylinder's axis, and the liquid cylinder is fixed to a static frame;

[0081] • A hydraulic piston that can be translated hermetically within a liquid cylinder to form a variable hydraulic volume, which is wholly or partially filled with working fluid.

[0082] • A gas and liquid reservoir connected via a connecting conduit to a variable hydraulic volume, such that the reservoir is primarily or entirely filled with working fluid when the variable hydraulic volume is at its minimum, and partially or entirely filled with working gas when the variable hydraulic volume is at its maximum, wherein the change in the absolute volume of the working gas contained in the variable pneumatic volume forms the variable pneumatic volume on the one hand, and on the other hand is approximately equal to the change in the absolute volume of the working fluid contained in the variable hydraulic volume.

[0083] • A heat exchange and accumulation component housed in a gas and liquid reservoir, the component being capable of exchanging heat with the working gas or working liquid on the one hand, and temporarily storing all or part of the heat on the other hand;

[0084] • A heat-exporting or heat-inputting component that directly or indirectly absorbs heat or directly or indirectly transfers heat to a heat exchange and accumulation component, and / or to a working liquid, and / or to a working gas, wherein the absorbed heat is then transferred to a heating component, or the transferred heat has been previously absorbed to a cooling component, wherein the heating component and the cooling component are located outside the gas and liquid reservoir;

[0085] • A filling member that allows or prevents working gas from being transferred from the intake chamber to the gas and liquid reservoir via the inlet port;

[0086] • Discharge member, which allows or prevents working gas from being transferred from the gas and liquid reservoir to the pressure relief chamber via the outlet port;

[0087] • Connecting rod, the first end of which is securely fixed to the hydraulic piston, the rod being approximately parallel to the longitudinal axis of the piston;

[0088] • A piston guide member that maintains the hydraulic piston and connecting rod parallel to the cylinder, regardless of the piston's position within the cylinder;

[0089] • A crankshaft that can rotate about an axis parallel to an inclined axis in at least one shaft bearing, and the crankshaft having at least one crank, about which a second end of a connecting rod is articulated;

[0090] • At least one drive motor that directly or indirectly rotates the crankshaft;

[0091] • Kinetic energy storage component, which is directly or indirectly connected to the crankshaft.

[0092] The mechanical liquid piston slow expansion compressor according to the invention includes an inclined shaft that is a tubular ball joint terminating a liquid cylinder, and the interior of the tubular ball joint wholly or partially forms a communicating conduit, the ball joint being capable of hermetically pivoting within a concave ball joint housing fixed to a gas and liquid reservoir.

[0093] The mechanical liquid piston slow expansion compressor according to the invention includes a tubular ball joint that receives at its center a ball joint shaft parallel to an inclined axis, the shaft being articulated about a ball joint tubing bundle directly or indirectly fixed to a gas and liquid reservoir.

[0094] The mechanical liquid piston slow expansion compressor according to the invention includes a spherical joint tube bundle connected to a gas and liquid reservoir by means of a tube bundle connection that allows articulation, the tube bundle being rotatable about the tube bundle connection.

[0095] The mechanical liquid piston slow expansion compressor according to the invention includes a liquid cylinder and a gas and liquid reservoir, the liquid cylinder and the gas and liquid reservoir forming a rigid assembly that pivots about an inclined axis.

[0096] The mechanical liquid piston slow expansion compressor according to the present invention includes a heat exchange and accumulation component, which is composed of a porous medium having pores, wherein a working liquid and a working gas alternately enter and exit the porous medium.

[0097] The mechanical liquid piston slow expansion compressor according to the invention includes a heat export and import component consisting of a circulation section of working liquid, which exits from a liquid cylinder or from a gas and liquid reservoir via a liquid outlet conduit to return to the cylinder or reservoir via a liquid inlet conduit, after heat has been transferred to a heating component or after heat has been drawn to a cooling component.

[0098] The mechanical liquid piston slow expansion compressor according to the invention includes a heat export or import component consisting of at least one heat exchanger conduit housed in a gas and liquid reservoir, and a heat transfer fluid circulating in the at least one heat exchanger conduit, which transfers heat drawn or transferred to the heat exchange and accumulation component, and / or to the working liquid, and / or to the working gas via the heat transfer conduit all the way to the cooling component or the heating component.

[0099] The mechanical liquid piston slow expansion compressor according to the present invention includes a heat exchange and accumulation component consisting of at least one liquid spray nozzle supplied by a liquid spray pump, the nozzle being capable of atomizing the working liquid into fine droplets within the internal volume of a gas and liquid reservoir.

[0100] The mechanical liquid piston slow expansion compressor according to the present invention includes an inclined shaft, which is composed of: a rolling track fixed to a static frame and a rolling surface that can roll on the rolling track, the rolling track being directly or indirectly fixed to a liquid cylinder; and a rolling track gear whose base circle coincides with the contact line between the rolling track and the rolling surface that is directly or indirectly fixed to the liquid cylinder, fixed to the static frame, and engaging with the rolling surface gear.

[0101] The mechanical liquid piston slow expansion compressor according to the present invention includes a piston guide member consisting of a sliding pivot connection formed between an outer cylindrical surface of a connecting rod and a sliding ring fixedly connected to a liquid cylinder by means of an annular carrier structure.

[0102] The mechanical-liquid piston-type slow-expansion compressor according to the present invention includes a piston guide member consisting of a guide skirt disposed around the periphery of a hydraulic piston, the skirt being capable of translating within the cylinder with a low clearance.

[0103] The mechanical-liquid reciprocating slow-expansion compressor according to the invention includes a filling member and / or a discharge member, which are constituted by at least one compressor vane and / or at least one controlled compressor valve. However, in operation, the working gas is discharged from the reservoir via a pressure relief chamber at a pressure greater than the pressure at which it was previously introduced into the gas and liquid reservoir via the inlet chamber, while a heat export or import member transfers heat to a heating member, such that a variable pneumatic volume is formed in the compressor.

[0104] The mechanical-liquid piston slow-expansion compressor according to the invention includes a filling member and / or a discharge member, which are constituted by at least one controlled expansion valve. However, in operation, the working gas is discharged from the reservoir via a pressure relief chamber at a pressure lower than that at which it was previously introduced into the gas and liquid reservoir via the inlet chamber, while the heat export or import member draws heat to the cooling member, such that a variable pneumatic volume is formed in the expander.

[0105] The mechanical liquid reciprocating slow expansion compressor according to the invention includes a pressure relief chamber of the compressor connected to the inlet chamber of the expander via a high-pressure gas conduit, such that working gas depressurized via the pressure relief chamber of the compressor is introduced into the expander via the inlet chamber of the expander, the crankshaft of the compressor being directly or indirectly connected to the crankshaft of the expander, and the compressor and the expander being coupled to form a heat pump.

[0106] The mechanical liquid piston slow expansion compressor according to the invention includes a high-pressure gas conduit connected to at least one high-pressure gas reservoir.

[0107] The mechanical liquid piston slow expansion compressor according to the present invention includes an inlet chamber of the compressor and a pressure relief chamber of the expander, the inlet chamber and the pressure relief chamber being connected by means of a low-pressure gas reservoir, the inlet chamber and the pressure relief chamber being respectively connected to the low-pressure gas reservoir through low-pressure gas conduits.

[0108] The mechanical liquid reciprocating slow expansion compressor according to the invention includes an inlet chamber and a pressure relief chamber, which are located in the upper portion of a gas and liquid reservoir, which is itself located above a liquid cylinder, such that, due to gravity, the working gas always exits the gas and liquid reservoir first through the pressure relief chamber, and the working liquid always enters the reservoir first through the inlet chamber.

[0109] The mechanical liquid piston slow expansion compressor according to the invention includes an inclined shaft formed by a hollow cylindrical shaft having at least one open radial space, the cylindrical shaft being positioned above a gas and liquid reservoir, and an inlet chamber and / or a pressure relief chamber being connected to an annular gas collector surrounding the cylindrical shaft, the annular gas collector including an open radial space such that working gas can circulate between the hollow cylindrical shaft and the inlet chamber and / or pressure relief chamber via the open radial space and the annular gas collector.

[0110] The mechanical liquid piston slow expansion compressor according to the present invention includes a kinetic energy storage component consisting of a low-speed inertial flywheel, which is rotatably fixed to a crankshaft on one side and rotatably fixed to a ring gear on the other side. A drive motor rotates the ring gear by means of at least one ring drive pinion, the base circle diameter of which is smaller than the base circle diameter of the ring. The ring and the pinion form a high transmission ratio meshing system. However, a high-speed inertial flywheel is rotatably fixed to the ring drive pinion directly or indirectly.

[0111] The mechanical liquid piston type slow expansion compressor according to the present invention includes a liquid spray pump, which is composed of: a pump cylinder disposed in a liquid cylinder and / or in an extension of the cylinder; and a pump piston movable by a hydraulic piston and / or by the liquid cylinder, the pump piston being capable of translation within the pump cylinder.

[0112] The mechanical liquid piston type slow expansion compressor according to the present invention includes a pump piston, which includes a stroke start contact pin, by means of which the pump piston moves and the piston returns to the stroke end contact portion by piston return mass.

[0113] The mechanical liquid piston type slow expansion compressor according to the present invention includes a pump piston that moves by means of a moving spring.

[0114] The mechanical liquid piston slow expansion compressor according to the invention includes an overflow pump that transfers a small amount of working fluid from an overflow reservoir to a gas and liquid reservoir and / or a liquid cylinder each time the crankshaft rotates.

[0115] The mechanical liquid reciprocating slow expansion compressor according to the invention includes an overflow reservoir in communication with a pressure relief chamber, wherein the working gas pressure in the reservoir is close to or equal to the working gas pressure in the pressure relief chamber.

[0116] The mechanical-liquid reciprocating slow-expansion compressor according to the invention includes an overflow pump comprising a pump blind cylinder, an overflow pump piston being hermetically translatable within the pump blind cylinder, the overflow pump piston and the cylinder forming a variable overflow pump volume, the variable overflow pump volume being filled with working fluid from an overflow reservoir via at least one overflow pump inlet vane when it increases, and the variable overflow pump volume being depressurized via a pressure relief valve to release the fluid to a gas and liquid reservoir and / or a liquid cylinder when it decreases.

[0117] The mechanical liquid piston slow expansion compressor according to the invention includes an overflow pump piston, which is a double-body staged piston. The double-body staged piston includes a large-diameter body having a face with a large cross-section forming one of the walls of a variable overflow pump volume. The staged piston also includes a small-diameter body axially opposite the face with the large cross-section, the small-diameter body being hermetically translatable within an actuating cylinder whose internal volume is directly or indirectly connected to the internal volume of a liquid cylinder. The small-diameter body includes a face with a small cross-section, on which pressure in the liquid cylinder is applied. The staged piston also provides a face with an average cross-section at the junction between the large-diameter body and the small-diameter body, from which the small-diameter body protrudes. The face with the average cross-section is connected to an overflow reservoir and is subjected to pressure in the reservoir. The staged piston abutment fixes the maximum volume of the variable overflow pump volume, and a double-body piston return spring tends to push against the double-body staged piston in the direction of the face with the large cross-section of the double-body staged piston.

[0118] The mechanical-liquid reciprocating slow-expansion compressor according to the invention includes a pressure relief valve comprising a valve actuator piston that is hermetically translatable within a valve actuator cylinder. The valve actuator piston initially has a valve actuation axial face communicating with an overflow reservoir, and pressure in the reservoir is applied to this valve actuation axial face. When the valve actuator piston moves in the direction of this face, the face enables an overflow vane to rise from an overflow vane seat. This has the effect of communicating a variable overflow pump volume via the overflow vane with a gas and liquid reservoir and / or a liquid cylinder. The valve actuation... The actuator piston has a liquid cylinder-side axial surface that communicates with the liquid cylinder. The pressure in the cylinder is applied to this liquid cylinder-side axial surface. When the valve actuator piston moves in the direction of this liquid cylinder-side axial surface, the liquid cylinder-side axial surface can contact the liquid cylinder-side abutment. However, the actuator piston return spring tends to push the valve actuator piston in the direction of the valve actuator piston's valve actuation axial surface, and the overflow vane return spring tends to return the overflow vane to contact its engaged overflow vane seat. The force generated by the actuator piston return spring is greater than the force generated by the overflow vane return spring.

[0119] The mechanical liquid piston slow expansion compressor according to the invention includes an overflow pump piston, which is a double-body staged piston. The double-body staged piston includes a large-diameter body having a surface with a large cross-section connected to and subjected to pressure in an overflow reservoir. The staged piston also includes a small-diameter body axially opposite the surface with the large cross-section. This small-diameter body is hermetically translatable within an actuating cylinder whose internal volume is directly or indirectly connected to the internal volume of a liquid cylinder. The small-diameter body includes a surface with a small cross-section, on which pressure in the liquid cylinder is applied. A surface with an average cross-section exists at the junction between the large-diameter body and the small-diameter body, from which the small-diameter body protrudes. This surface forms one wall of a variable overflow pump volume. A staged piston abutment fixes the maximum volume of the variable overflow pump volume, and a double-body piston return spring tends to push against the double-body staged piston in the direction of the surface with the small cross-section.

[0120] The mechanical-liquid reciprocating slow-expansion compressor according to the invention includes a pressure relief valve comprising a valve actuator piston that is hermetically translatable within a valve actuator cylinder. The valve actuator piston initially has a valve actuation axial face communicating with a liquid cylinder, and pressure in the cylinder is applied to this valve actuation axial face. When the valve actuator piston moves in the direction of this face, the face enables the overflow vanes of an overflow vane seat to rise. This has the effect of communicating a variable overflow pump volume via the overflow vanes with a gas and liquid reservoir and / or the liquid cylinder. The valve actuator piston... The plug has a reservoir-side axial surface that communicates with an overflow reservoir. Pressure in the reservoir is applied to this reservoir-side axial surface, and when the valve actuator piston moves in the direction of this reservoir-side axial surface, this reservoir-side axial surface can contact the overflow reservoir-side abutment. However, the actuator piston return spring tends to push the valve actuator piston in the direction of the valve actuator piston's valve actuation axial surface, and the overflow vane return spring tends to return the overflow vane to contact its engaged overflow vane seat. The force generated by the actuator piston return spring is greater than the force generated by the overflow vane return spring.

[0121] The mechanical liquid piston slow expansion compressor according to the invention includes a balancing member that wholly or partially replaces the piston guide member to tilt the liquid cylinder during crankshaft rotation.

[0122] The mechanical liquid piston slow expansion compressor according to the present invention includes a balancing member consisting of a balancing mast. The balancing mast includes a balancing mass on one hand and articulates about a mast axis that is parallel to the liquid cylinder and fixed to a static frame on the other hand. However, the balancing mast forms a pivot-sliding joint with the cylinder and constitutes an imbalance opposite to that of the cylinder.

[0123] The following description, given with reference to the accompanying drawings and as a non-limiting example, will enable a best understanding of the invention, its features, and the advantages it can provide:

[0124] [ Figure 1 [Illustration] is a cross-sectional view of a specific configuration of a mechanical liquid piston slow expansion compressor according to the present invention, wherein the tilting axis of the liquid cylinder is a tubular ball joint, the interior of which forms a connecting conduit wholly or partially, and the tubular ball joint can be pivotally and sealingly fixed in a concave ball joint housing to a gas and liquid reservoir.

[0125] [ Figure 2 [Image] is a cross-sectional view of a mechanical liquid reciprocating slow-expansion compressor according to the present invention, wherein the liquid cylinder and the gas and liquid reservoir of the mechanical liquid reciprocating slow-expansion compressor form a rigid assembly that pivots about an inclined axis.

[0126] [ Figure 3 [This refers to a variant of the mechanical liquid piston slow expansion compressor according to the invention, such as...] Figure 2 The three-dimensional cross-sectional view of the rigid assembly shown shows the overflow pump coupled to the gas and liquid reservoirs.

[0127] [ Figure 4 There is no overflow pump. Figure 3 The three-dimensional exploded view of the rigid component shown.

[0128] [ Figure 5 [The diagram shows the pressure-volume cycle of a heat pump consisting of a compressor and an expander, each formed by a mechanical liquid piston slow-expansion compressor according to the invention.]

[0129] [ Figure 6 [This is a three-dimensional assembly view from the front of a heat pump consisting of a compressor and an expander, each formed by a mechanical liquid piston slow expander according to the invention.]

[0130] [ Figure 7 ] is from Figure 6 The image shows a three-dimensional assembly view of the heat pump from the rear.

[0131] [ Figure 8 ]yes Figure 6The image shows a three-dimensional cross-sectional view of a heat pump.

[0132] [ Figure 9 [ ] is a schematic diagram of the environment and accessories of a heat pump consisting of a compressor and an expander, the compressor and the expander being formed by a mechanical liquid piston slow expansion compressor according to the present invention.

[0133] [ Figure 10 [Illustrated cross-sectional view of a liquid spray pump of a compressor formed by a mechanical liquid piston slow expansion compressor according to the present invention, wherein the pump piston of the spray pump moves in a pump cylinder by a hydraulic piston, the pump piston being in the process of drawing working liquid under the action of piston return mass, and the pump inlet vanes included in the pump piston are shown enlarged in the illustration.]

[0134] [ Figure 11 ] is shown in Figure 10 A schematic cross-sectional view of what happens next, at which point the pump piston contacts the end of its suction stroke; however, the hydraulic piston of the compressor in the mechanical-liquid piston type slow expansion compressor according to the invention has finished its descent stroke and begun its ascent stroke.

[0135] [ Figure 12 ] is shown in Figure 11 A schematic cross-sectional view of what happens next, where the hydraulic piston of the compressor of the mechanical liquid piston type slow expansion compressor according to the invention contacts the stroke start point of the pump piston again to force the pump piston to push against the... Figure 10 The working fluid has been drawn into the liquid spray nozzle via a pump depressurization vane, which is shown enlarged in the illustration.

[0136] [ Figure 13 [Illustrated cross-sectional view of a liquid spray pump of an expander formed by a mechanical liquid piston slow expander compressor according to the invention, wherein the pump piston of the liquid spray pump moves in a pump cylinder by means of a hydraulic piston and a moving spring, the pump piston being in the process of drawing working liquid via pump inlet vanes included in the pump cylinder, the vanes being shown enlarged in the illustration.]

[0137] [ Figure 14 ] is shown in Figure 13 A schematic cross-sectional view of what happens next, at which point the pump piston comes into contact with the end of the suction stroke; however, the hydraulic piston of the expander of the mechanical liquid piston type slow expander compressor according to the invention has continued its upward stroke by compressing the moving spring and has not yet begun its downward stroke.

[0138] [ Figure 15 ] is shown in Figure 14A schematic cross-sectional view of what happens next, at which point the hydraulic piston of the expander of the mechanical liquid piston type slow expander compressor according to the invention has begun its downward stroke, which has the effect of releasing the compression of the moving spring, and the pump piston remains in contact with the end of its upward stroke.

[0139] [ Figure 16 ] is shown in Figure 15 A schematic cross-sectional view of what happens next, at which point the moving spring has expanded to such that the hydraulic piston of the expander of the mechanical liquid piston type slow expander compressor according to the invention has driven the pump piston in its movement and has forced the pump piston to... Figure 13 The working fluid, which has been drawn into the liquid spray nozzle via the pump depressurization vane, is shown enlarged in the illustration.

[0140] [ Figure 17 [A] is a three-dimensional cross-sectional view of the overflow pump and overflow reservoir provided for a compressor formed by a mechanical liquid piston slow expansion compressor according to the present invention.

[0141] [ Figure 18 [Illustrated cross-sectional view of an overflow pump for a compressor formed by a mechanical liquid piston slow expansion compressor according to the invention, wherein the pressure in the overflow reservoir of the pump is greater than the pressure in the liquid cylinder, which has the function of filling the variable overflow pump volume with working fluid from the overflow reservoir.]

[0142] [ Figure 19 ] is shown in Figure 18 A schematic cross-sectional view of what happens next, at which point the pressure in the overflow reservoir of the overflow pump of the compressor formed by the mechanical liquid piston slow expansion compressor according to the invention becomes substantially equal to the pressure in the liquid cylinder, which causes the double-body piston return spring to move the overflow pump piston to discharge the working fluid previously drawn into the variable overflow pump volume into the liquid cylinder.

[0143] [ Figure 20 [Illustrated cross-sectional view of an overflow pump for an expander formed by a mechanical liquid piston slow expander compressor according to the invention, wherein the pressure in the overflow reservoir of the pump is less than the pressure in the liquid cylinder, which has the function of filling the variable overflow pump volume with working fluid from the overflow reservoir.]

[0144] [ Figure 21 ] is shown in Figure 20A schematic cross-sectional view of what happens next, at which point the pressure in the overflow reservoir of the overflow pump of the expander formed by the mechanical liquid piston slow expander compressor according to the invention becomes substantially equal to the pressure in the liquid cylinder, which causes the double-body piston return spring to move the overflow pump piston to discharge the working fluid previously drawn into the variable overflow pump volume into the liquid cylinder.

[0145] [ Figure 22 [Image] is a side view of a variant of a mechanical liquid piston slow expansion compressor according to the invention, in which a liquid cylinder and a gas and liquid reservoir form a rigid assembly that pivots about an inclined axis consisting of a rolling track fixed to a static frame, on which a rolling surface fixed to the gas and liquid reservoir can roll, the rolling track being connected to a rack and pinion that engage with a rolling surface gear connected to the rolling surface.

[0146] [ Figure 23 [Illustration] is a side view of a variant of a mechanical liquid piston slow expansion compressor according to the invention, according to which a balancing member engages with a piston guide member to tilt during crankshaft rotation, a rigid assembly is formed of a liquid cylinder and gas and liquid reservoirs, the balancing member being constituted by a balancing mast whose balancing mass creates an imbalance opposite to the balancing mass of the assembly. Detailed Implementation

[0147] exist Figures 1 to 23 The mechanical liquid piston slow expansion compressor 1 according to the present invention, various details of its components, its variations and its accessories have been shown.

[0148] As can be seen, especially in Figures 1 to 3 In China Figure 8 China and in Figures 10 to 16 In this process, a mechanical liquid reciprocating slow-expansion compressor 1 defines a variable pneumatic volume 2, which forms a compressor 3 or an expander 4, and the working gas 5 can enter the volume 2 via an inlet port 6 or leave the volume 2 via an outlet port 7.

[0149] Figures 1 to 4 , Figures 6 to 8 , Figures 10 to 16 as well as Figure 22 and Figure 23 A mechanical liquid piston slow expansion compressor 1 according to the invention is shown, comprising a liquid cylinder 8, which is pivotable directly or indirectly about an inclined shaft 9 perpendicular to the axis of the cylinder 8, and the liquid cylinder is fixed to a static frame 40. According to the provided pivoting mechanism of the cylinder 8, the shaft 9 is movable relative to the frame 40 according to the inclination of the liquid cylinder 8. The liquid cylinder is advantageously able to receive a thermal insulation layer 59 to avoid heat exchange with the surrounding environment.

[0150] It should be noted that the tilting shaft 9 can accommodate at least one roller bearing 105, as in Figure 4 China and in Figures 6 to 8 Specifically shown, or accepting at least one ball bearing or needle roller bearing known in itself, while the static frame 40 may, for example, be fixed or placed on the floor of a residential, commercial or industrial building 121.

[0151] As in Figures 1 to 4 In China Figure 8 China and in Figures 10 to 16 As can be seen, the mechanical liquid piston type slow expansion compressor 1 according to the present invention includes a hydraulic piston 10 that is hermetically translatable in a liquid cylinder 8 to form a variable hydraulic volume 12 with the liquid cylinder, the variable hydraulic volume being wholly or partially filled with working fluid 13.

[0152] It should be noted that the maximum acceleration or deceleration experienced by the hydraulic piston 10 between its midpoint and its neutral position must preferably be less than the Earth's gravity, so that the working fluid 13 always remains in complete contact with the piston 10, and that cavitation or excessive mixing does not occur between the working gas 5 and the working fluid 13.

[0153] exist Figures 1 to 3 In China Figure 8 China and in Figures 10 to 16 It should be noted that the hydraulic piston 10 may advantageously include at least one seal 51, whether the seal is an O-ring, lip seal, composite seal or a seal of a type known to those skilled in the art, the seal 51 preventing leakage of the working fluid 13 between the piston 10 and the liquid cylinder 8.

[0154] As an alternative to the seal 51, at least one cut or continuous metal segment may form a seal between the hydraulic piston 10 and the liquid cylinder 8. However, the working fluid 13 may be, for example, composed of pure water, or may be supplemented with ethylene glycol to lower the freezing temperature of the water.

[0155] exist Figures 1 to 3 In China Figure 8 China and in Figures 10 to 16The mechanical liquid piston slow expansion compressor 1 according to the invention also includes a gas and liquid reservoir 14, which is connected to a variable hydraulic volume 12 via a connecting conduit 15, such that the reservoir 14 is mainly or entirely filled with working liquid 13 when the variable hydraulic volume 12 is at its minimum, and is partially or entirely filled with working gas 5 when the variable hydraulic volume 12 is at its maximum. According to the principle of communicating vessels, the change in the absolute volume of the working gas 5 contained in the variable pneumatic volume 2 forms the variable pneumatic volume 2 on the one hand, and on the other hand is approximately equal to the change in the absolute volume of the working liquid 13 contained in the variable hydraulic volume 12.

[0156] It should be noted that the gas and liquid reservoir 14 can advantageously accommodate external thermal insulation to avoid heat exchange with the surrounding environment.

[0157] Figures 1 to 4 as well as Figures 8 to 16 The mechanical liquid piston slow expansion compressor 1 according to the invention also includes a heat exchange and accumulation component 16, which is housed in a gas and liquid reservoir 14. The component 16 is capable of exchanging heat with the working gas 5 or the working liquid 13 on the one hand, and temporarily storing all or part of the heat on the other hand.

[0158] In the same description Figures 1 to 4 as well as Figures 8 to 16 The mechanical liquid piston slow expansion compressor 1 according to the invention has been shown to include a heat extraction or input member 17 that directly or indirectly extracts heat or directly or indirectly transfers heat to a heat exchange and accumulation member 16, and / or to a working liquid 13, and / or to a working gas 5. The extracted heat is then transferred to a heating member 18, or the transferred heat has been previously extracted to a cooling member 19, which is outside a gas and liquid reservoir 14. Based on the principles typically used for air-heat or geothermal heat pumps, it can take the form of an underfloor heating and cooling device 106 installed in a commercial or residential building 121, a fan coil unit known per se, or an air-to-water, soil-to-water, or water-to-water exchanger 107 installed on the exterior 122.

[0159] As in Figures 1 to 4 China and in Figures 10 to 16 As can be seen in the figure, the mechanical liquid piston slow expansion compressor 1 according to the present invention also includes a filling member 20, which allows or prevents the working gas 5 from being transferred from the intake chamber 21 to the gas and liquid reservoir 14 via the inlet port 6.

[0160] Figures 1 to 4 as well as Figures 10 to 16The mechanical liquid piston slow expansion compressor 1 according to the invention also includes a discharge member 22, which allows or prevents the working gas 5 from being transferred from the gas and liquid reservoir 14 to the pressure relief chamber 62 via the outlet port 7.

[0161] exist Figures 1 to 4 , Figures 6 to 8 , Figures 10 to 16 China and in Figure 22 and Figure 23 It should be noted that the mechanical liquid piston type slow expansion compressor 1 according to the present invention includes a connecting rod 11, the first rod end 29 of which is firmly fixed to the hydraulic piston 10, and the rod 11 is approximately parallel to the longitudinal axis of the piston 10.

[0162] As in Figures 1 to 3 In China Figure 8 China and in Figures 10 to 16 As can be clearly seen, the mechanical liquid piston type slow expansion compressor 1 according to the present invention includes a piston guide member 23, which maintains the hydraulic piston 10 and the connecting rod 11 parallel to the cylinder 8, regardless of the position of the piston 10 in the cylinder 8;

[0163] Figure 1 and Figure 2 , Figures 6 to 9 as well as Figure 22 and Figure 23 The mechanical liquid piston slow expansion compressor 1 according to the invention is also shown to include a crankshaft 24 or eccentric shaft known per se, which is rotatable about an axis parallel to the inclined shaft 9 in at least one bearing 25, and the crankshaft or eccentric shaft has at least one crank 26, about which the second rod end 30 of the connecting rod 11 is articulated.

[0164] In the same figures, it should be noted that, advantageously, the crankshaft 24 can rotate in the shaft bearing 25, and / or the second rod end 30 can articulate about the crank 26 by means of a roller bearing 105, ball bearing or needle roller bearing known per se.

[0165] exist Figure 1 , Figure 2 , Figure 6 , Figure 22 and Figure 23 It can also be seen that the mechanical liquid piston slow expansion compressor 1 according to the present invention includes at least one drive motor 27, which directly or indirectly rotates the crankshaft 24. The motor 27 can be electric, thermal, hydraulic, pneumatic or any other type known to those skilled in the art, achieved by internal or external combustion.

[0166] Finally, and as Figure 1 , Figure 2 , Figure 6 , Figure 7 , Figure 8 , Figure 22 and Figure 23 As shown, the mechanical liquid piston type slow expansion compressor 1 according to the present invention further includes a kinetic energy storage component 28, which is directly or indirectly connected to the crankshaft 24.

[0167] exist Figure 1 As shown in the figure, in a variant of the mechanical liquid piston slow expansion compressor 1 according to the invention, the tilting shaft 9 may be a tubular ball joint 111 that terminates the liquid cylinder 8, and the interior of the tubular ball joint forms a connecting conduit 15 wholly or partially. The ball joint 111 is capable of pivoting in a sealed manner within a concave ball joint housing 123 fixed to the gas and liquid reservoir 14.

[0168] Furthermore, it should be noted that this configuration is reversible, i.e., the tubular ball joint 111 can terminate the gas and liquid reservoir 14, while the concave ball joint housing 123 can be fixed to the liquid cylinder 8.

[0169] It should also be noted that the inner diameter of the liquid cylinder 8 can be advantageously set to be less than or equal to the outer diameter of the tubular ball joint 111, which forms a seal with the concave ball joint housing 123. This avoids the pressure in the liquid cylinder 8 and in the gas and liquid reservoir 14 exerting a force on the liquid cylinder 8 that would tend to move the liquid cylinder away from the gas and liquid reservoir 14.

[0170] exist Figure 1 It should also be noted that the concave spherical joint housing 123 can receive a seal 51 made of abrasion-resistant material (such as polytetrafluoroethylene filled with anti-friction particles) at the equator of the tubular spherical joint 111.

[0171] As in Figure 1 As can still be seen, the concave spherical connector housing 123 can receive a slit circular pad 127 made of an anti-friction material (such as bronze or "Teflon"), the slit circular pad being able to be installed around the tubular spherical connector 111 through the slits of the pad 127.

[0172] according to Figure 1 The variant of the mechanical liquid piston slow expansion compressor 1 shown according to the invention has a tubular ball joint 111 that can receive a ball joint shaft 124 parallel to the inclined axis 9 at its center. The shaft 124 is articulated about a ball joint tube bundle 125 that is directly or indirectly fixed to the gas and liquid reservoir 14. The center of the ball joint shaft 124 and the center of the inclined axis 9 are coincident.

[0173] Note that the spherical connector tube bundle 125 maintains a constant distance between the liquid cylinder 8 and the gas and liquid reservoir 14. The tube bundle 125 engages with a slit circular pad 127, which holds the tubular spherical connector 111 at the center of the concave spherical connector housing 123.

[0174] It should also be noted that the spherical joint shaft 124 and its anchoring in the tubular spherical joint 111 must preferably be compact and have a hydrodynamic shape that facilitates low resistance to the passage of the working fluid 13 circulating between the liquid cylinder 8 and the gas and liquid reservoir 14.

[0175] It should also be noted that the spherical joint shaft 124 can be a simple pivot connection, a universal connection, or a spherical joint connection.

[0176] Still in accordance with Figure 1 In a variant of the embodiment of the mechanical liquid piston slow expansion compressor 1 according to the invention shown, the spherical joint tube bundle 125 can be connected to the gas and liquid reservoir 14 by means of an articulated tube bundle connection 126, the tube bundle 125 being rotatable about the articulated tube bundle connection.

[0177] Figure 1 , Figure 2 , Figure 6 , Figure 7 , Figure 8 as well as Figures 10 to 16 Another variant of the mechanical liquid piston slow expansion compressor 1 according to the invention is shown, wherein the liquid cylinder 8 and the gas and liquid reservoir 14 can form a rigid assembly 31 that pivots about an inclined axis 9, in which case the connecting conduit 15 is formed by a junction area included between the cylinder 8 and the reservoir 14, and is not required to have the same diameter as the reservoir.

[0178] It should be noted that, according to the aforementioned variant, the flexible conduit may advantageously connect the inlet chamber 21 and / or the pressure relief chamber 62 to, for example, a high-pressure gas reservoir 58 or a low-pressure gas reservoir 60, or the gas and liquid reservoir 14 may be connected to the heating element 18 and / or the cooling element 19.

[0179] As in Figures 10 to 16 As shown in the diagram, the heat exchange and accumulation component 16 may be composed of a porous medium 32 having pores 33, through which the working liquid 13 and the working gas 5 alternately enter and exit.

[0180] As an example, the porous medium 32 may be made of porous ceramic, a ceramic or metal structure, or a metal straw made of copper or aluminum.

[0181] Figures 10 to 16It is also shown that the heat export or import component 17 may be composed of a circulation portion of the working fluid 13, which exits from the liquid cylinder 8 or from the gas and liquid reservoir 14 via a liquid outlet conduit 34, and returns to the liquid cylinder 8 or the reservoir 14 via a liquid inlet conduit 35, after heat has been transferred to the heating component 18 or after heat has been drawn to the cooling component 19.

[0182] It should be noted that in this case, the undisclosed circulation solenoid valve can regulate the flow rate of the working fluid 13 transmitted to the liquid outlet conduit 34 and the liquid inlet conduit 35.

[0183] As another variation of the embodiment of the mechanical liquid piston slow expansion compressor 1 according to the present invention, in Figures 1 to 4 In China Figure 8 and Figure 9 China and in Figure 17 The diagram shows that the heat outlet or intake component 17 may be composed of at least one heat exchanger conduit 36, which is housed in a gas and liquid reservoir 14, and a heat transfer fluid 37 circulates in the at least one heat exchanger conduit, which transfers the heat drawn or transferred to the heat exchange and accumulation component 16, and / or to the working liquid 13, and / or to the working gas 5 via the heat transfer conduit 38 all the way to the cooling component 19 or the heating component 18.

[0184] It should be noted that in this case, the heat exchanger duct 36 itself can form the heat exchange and accumulation component 16.

[0185] As an example, the heat exchanger conduit 36 ​​may take the form of a copper or aluminum coil 109; however, the heat transfer conduits 38 are coated with a thermally insulating material on the portion of their inclusion between a gas and liquid reservoir 14 on one side and a cooling member 19 or a heating member 18 on the other side.

[0186] It should be noted that the coils or layers that the heat exchanger conduits 36 can form can be maintained in the proper position and abut against each other in the gas and liquid reservoirs 14 by a maintaining plate or a partition baffle 110. The maintaining plate or the partition baffle can form a flow guide and / or a flow restrictor, which generates a jet of the liquid 13 and / or the gas 5 during the passage of the working liquid 13 and / or the working gas 5 through the flow restrictor.

[0187] In addition, the heat exchanger duct 36 may accommodate external fins that increase its contact surface with the working liquid 13 or the working gas 5.

[0188] exist Figures 1 to 4 , Figure 8 and Figures 10 to 16As shown in the figure, according to a specific configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention, the heat exchange and accumulation member 16 may be composed of at least one liquid spray nozzle 71 supplied by a liquid spray pump 72, the nozzle 71 being capable of atomizing the working liquid 13 into fine droplets in the internal volume of the gas and liquid reservoir 14. The number, position and orientation of the nozzles 71 are not limited, and they are arranged such that the atomized working liquid 13 exposes a large expanded heat exchange surface to the working gas 5, while the driving speed of the liquid 13 on the gas 5 is also as conducive as possible to the heat exchange between the gas 5 and the liquid 13.

[0189] It should be noted that the liquid spray pump 72 may have one or more pistons, may be a gear pump, a turbine pump or a pump of a type known to those skilled in the art, and may be housed inside or outside the gas and liquid reservoir 14.

[0190] The liquid spray pump 72 may, for example, be composed of a piston that moves directly or indirectly via a cam rotated by a crankshaft 24, the profile of which is calculated such that the atomization of the working liquid 13 begins with a suitable angular momentum for rotating the shaft 24 and continues for a certain angular duration, conforming to an optimal intensity variation law.

[0191] It should be noted that, preferably, the liquid spray pump 72 draws the working liquid 13 into the liquid cylinder 8 and / or the gas and liquid reservoir 14 before depressurizing the liquid 13 via the liquid spray nozzle 71, so that the pressure difference between the intake and depressurization of the pump 72 is minimized.

[0192] exist Figure 22 As shown in the figure, in another variant of the mechanical liquid piston slow expansion compressor 1 according to the invention, the tilting shaft 9 may be composed of: a rolling track 41, which is fixed to the static frame 40 and the rolling surface 42, which is directly or indirectly fixed to the liquid cylinder 8, can roll on the rolling track; a rolling track gear 43 or rack and pinion, the base circle 44 of which coincides with the contact line between the rolling track 41 and the rolling surface 42, which is directly or indirectly fixed to the liquid cylinder 8, fixed to the static frame 40, and engages with the rolling surface gear 45 or rack and pinion.

[0193] This particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention enables the limitation of losses caused by friction at the tilting shaft 9, while synchronizing the angular positioning of the liquid cylinder 8 relative to the static frame 40.

[0194] It should be noted that in this case, a retaining flange may be provided, which is fixed to the liquid cylinder 8, and if the pressure in the cylinder 8 is insufficient to maintain the rolling track 41 in contact with the rolling surface 42, the retaining flange may contact the static frame 40.

[0195] It should be noted that, depending on the geometry maintained for the rolling surface 42 and the rolling track 43, the tilting axis 9 of the liquid cylinder 8 can be moved relative to the static frame 40 by rotation according to the infinite kinematic laws.

[0196] As in Figures 1 to 3 In China Figures 6 to 8 In China Figures 10 to 16 China and in Figure 22 and Figure 23 As indicated in the document, the piston guide member 23 of the mechanical liquid piston slow expansion compressor 1 according to the invention may be constituted by a sliding pivot connection 47, which is formed between the outer cylindrical surface 48 of the connecting rod 11 and the sliding ring 49 fixedly connected to the liquid cylinder 8 by means of an annular carrier structure 50. According to a complementary variant of the embodiment of the mechanical liquid piston slow expansion compressor 1 according to the invention, the annular carrier structure may constitute a lubricant reservoir containing lubricant, which is responsible for lubricating the sliding ring 49 on the one hand and for lubricating one or more seals 51 that may be included around the hydraulic piston 10 on the other hand.

[0197] It should be noted that a lubricant sprayer or injector may be provided, which atomizes the lubricant inside the lubricant reservoir to ensure good distribution of the lubricant over all components requiring lubrication.

[0198] exist Figures 1 to 4 In China Figure 8 China and in Figures 10 to 16 As shown in the diagram, the piston guide member 23 may be composed of a guide skirt 57 disposed around the periphery of the hydraulic piston 10. The skirt 57 is capable of translating in the cylinder 8 with a low clearance to center the piston 10 in the cylinder 8, regardless of the axial position of the piston 10 in the cylinder 8.

[0199] exist Figures 1 to 4 China and in Figures 10 to 12 It has also been shown that the filling member 20 and / or the discharge member 22 may be composed of at least one compressor vane 52 and / or at least one controlled compressor valve 53. However, in operation, the working gas 5 is discharged from the gas and liquid reservoir 14 via the pressure relief chamber 62 at a pressure greater than the pressure at which it was previously introduced into the gas and liquid reservoir 14 via the intake chamber 21, while the heat export or import member 17 transfers heat to the heating member 18, so that the variable pneumatic volume 2 forms the compressor 3.

[0200] It should be noted that, based on the principles typically used in air-heat or geothermal heat pumps, the heating element 18 may be, for example, an underfloor heating device installed in a commercial or residential building 121, a fan coil unit known in itself, or an air-to-water, air-to-soil, or water-to-water exchanger installed on the exterior 122.

[0201] It should be noted that the compressor vane 52 may be formed by a single strip or contact portion returning to a seat sealed by a spring, regardless of the type of the single strip or contact portion, or by a valve assisted by an electromechanical actuator engaged with at least one pressure switch or with a pressure sensor coupled to the computer 120.

[0202] exist Figures 13 to 16 As shown, the filling member 20 and / or the discharge member 22 may be constituted by at least one controlled expander valve 54. However, in operation, the working gas 5 is discharged from the gas and liquid reservoir 14 via the pressure relief chamber 62 at a pressure lower than the pressure at which it was previously introduced into the gas and liquid reservoir 14 via the inlet chamber 21, while the heat export or import member 17 draws heat to the cooling member 19, so that the variable pneumatic volume 2 forms the expander 4.

[0203] It should be noted that, based on the principles typically used in air-heat or geothermal heat pumps, the cooling component 19 may be, for example, an underfloor cooling device installed in a commercial or residential building 121, a fan coil unit known in itself, or an air-to-water, air-to-soil, or water-to-water exchanger installed on the exterior 122.

[0204] according to Figures 6 to 9 The variant of the mechanical liquid piston slow expander compressor 1 shown according to the invention has a depressurization chamber 62 of compressor 3 connected to the inlet chamber 21 of expander 4 via a high-pressure gas conduit 56, such that working gas 5 depressurized via the depressurization chamber 62 of compressor 3 is introduced into expander 4 via the inlet chamber 21 of expander 4. The crankshaft 24 of compressor 3 is directly or indirectly connected to the crankshaft 24 of expander 4. Compressor 3 and expander 4 are coupled to form a heat pump 55, which performs a heat pump cycle close to Carnot's, i.e., quasi-adiabatic compression followed by quasi-isothermal compression performed in compressor 3, then quasi-adiabatic expansion, followed by quasi-isothermal expansion performed in expander 4.

[0205] According to this particular embodiment of the mechanical liquid piston slow expansion compressor 1 according to the invention, the crankshaft 24 of the compressor 3 and the crankshaft 24 of the expander 4 may be formed as a single and identical crankshaft 24 comprising at least two cranks 26, one of which is used for the compressor 3 and the other for the expander 4.

[0206] Alternatively, the crankshaft 24 of the compressor 3 may be indirectly connected to the crankshaft 24 of the expander 4 by means of a mechanical, electric, hydraulic, pneumatic transmission or any other transmission device.

[0207] It should be noted that, advantageously, the angular position of the crank 26 of the compressor 3 on the crankshaft 24 can be calculated relative to the angular position of the crank 26 of the expander 4 on the crankshaft 24, such that the resistance torque exerted by the compressor 3 on the crankshaft 24 is compensated as much as possible by the motor torque exerted by the expander 4 on the shaft 24, so that the drive motor 27 is subjected to the maximum motor torque or the lowest possible resistance.

[0208] exist Figure 9 It has also been shown that a high-pressure gas conduit 56 can be connected to at least one high-pressure gas reservoir 58, which can store hot and high-pressure working gas 5. The high-pressure gas conduit 56 and / or the high-pressure gas reservoir 58 are advantageously thermally insulated from their external environment by a thermal insulation layer 59.

[0209] Still in Figure 9 As shown in the diagram, the intake chamber 21 of the compressor 3 and the depressurization chamber 62 of the expander 4 can be connected by means of a low-pressure gas reservoir 60, which is connected to the intake chamber and the depressurization chamber respectively via a low-pressure gas conduit 61. The low-pressure gas reservoir 60 is capable of accumulating cold and relatively low-pressure working gas 5. The low-pressure gas conduit 61 and / or the reservoir 60 are advantageously thermally exposed to the environment to which the cooling member 19 is exposed, and can even form a low-pressure gas heat exchanger 39 wholly or partially, which forces the environment to transfer heat to the working gas 5.

[0210] Therefore, and as Figure 9 As shown, the circulating turbine 46 can force the working gas 5 contained in the low-pressure gas reservoir 60 to circulate in the low-pressure gas heat exchanger 39 included in the reservoir 60, while at least one electric fan 108 forces atmospheric air from the environment exposed to the cooling member 19 through the exchanger 39.

[0211] Advantageously, the pressure in the low-pressure reservoir 60 can be greater than atmospheric pressure, so that the heat pump 55 can be more compact.

[0212] It should be noted that, advantageously, in the case where the heat pump 55 formed by the mechanical liquid reciprocating slow expansion compressor 1 according to the invention includes a low-pressure gas reservoir 60, the working gas 5 may be different from atmospheric air and may be composed of any element or molecule (such as pure nitrogen, helium, argon or carbon dioxide), which is selected based on its chemical reactivity, its thermodynamic properties and its ability to facilitate heat exchange, particularly with the working liquid 13 and the heat exchange and accumulation member 16.

[0213] This also enables the prevention of corrosion of the components constituting the mechanical liquid piston type slow expansion compressor 1 according to the present invention, as well as the growth of microorganisms.

[0214] It should be noted that if the high-pressure gas reservoir 58 and the low-pressure gas reservoir 60 are thermally insulated from the external environment, they can form a total closed volume together with the heat pump 55, which stores energy in the form of pressure and / or heat, without converting the energy into useful heat or cold, thus contributing to the high efficiency of the pump 55.

[0215] exist Figures 1 to 4 In China Figures 6 to 8 In China Figures 10 to 16 China and in Figure 22 and Figure 23 It should be noted that the intake chamber 21 and the pressure relief chamber 62 are advantageously positioned in the upper portion of the gas and liquid reservoir 14, which itself is positioned above the liquid cylinder 8, such that due to gravity, the working gas 5 always exits the gas and liquid reservoir 14 first via the pressure relief chamber 62, and the working liquid 13 always enters the reservoir 14 first via the intake chamber. The working liquid 13 is always primarily held below the working gas 5 in the rigid component 31, even though the liquid 13 may contain a certain proportion of dissolved or bubbled gas 5.

[0216] according to Figures 2 to 4 , Figures 6 to 8 as well as Figures 10 to 16 In a specific variant of the embodiment of the mechanical liquid piston slow expansion compressor 1 according to the invention shown, the tilting shaft 9 may be constituted by a hollow cylindrical shaft 63 having at least one open radial space 64, the cylindrical shaft 63 being positioned above the gas and liquid reservoir 14, while the inlet chamber 21 and / or pressure relief chamber 62 are connected to an annular gas collector 65 surrounding the cylindrical shaft 63, and the annular gas collector including the open radial space 64, such that the working gas 5 can circulate between the interior of the hollow cylindrical shaft 63 and the inlet chamber 21 and / or pressure relief chamber 62 via the open radial space 64 and the annular gas collector 65.

[0217] It should be noted that the rotating shaft seal can be advantageously positioned axially on either side of the open radial space 64 and at the interface between the hollow cylindrical shaft 63 and the annular gas collector 65, the seal forming a seal against the working gas 5 between the shaft 63 and the collector 65.

[0218] As Figure 6 In a specific embodiment of the mechanical liquid piston slow expansion compressor 1 according to the invention, as detailed in the description, the kinetic energy storage member 28 may be composed of a low-speed inertial flywheel 66, which is rotatably fixed to the crankshaft 24 on one hand and rotatably fixed to the ring gear 67 on the other hand. The drive motor 27 rotates the ring gear by means of at least one ring drive pinion 68, the base circle diameter of which is smaller than the base circle diameter of the ring 67. The ring and the pinion 68 form a high transmission ratio meshing system 69. However, a high-speed inertial flywheel 70 is rotatably fixed directly or indirectly to the ring drive pinion 68.

[0219] According to this particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention, the instantaneous torque change applied to the crankshaft 24 by the compression or expansion of the working gas 5 in the gas and liquid reservoir 14 is mainly absorbed by the inertia of the low-speed inertial flywheel 66 and the inertia of the high-speed inertial flywheel 70, so that the torque resisting or driving the drive motor 27 is smooth, and the motor 27 is therefore mainly subjected to the average resistance torque necessary to maintain the regular rotation of the crankshaft 24.

[0220] Note that the high-speed inertial flywheel 70 may optionally be confined within a vacuum housing.

[0221] In this configuration, the power transmission between the flywheel 70 and the annular drive pinion 68 can be performed via non-contact magnetic coupling.

[0222] It should also be noted that, in order to facilitate the rotation of the assembly consisting of the low-speed inertia flywheel 66 and the crankshaft 24, the drive motor 27 is rotatably and securely fixed to the high-speed inertia flywheel 70. However, a separable coupling can be inserted between the assembly formed on one side by the motor 27 and the flywheel 70 and on the other side by the annular drive pinion 68. The coupling can be magnetic, hydraulic, or any other type.

[0223] exist Figure 1 , Figure 2 , Figure 6 , Figure 9 , Figure 22 and Figure 23 As shown in the diagram, the high gear ratio meshing system 69 can be advantageously inserted between the drive motor 27 and the ring drive pinion 68.

[0224] like Figure 3 and Figure 4 as well as Figures 10 to 16 As shown, the liquid spray pump 72 may be composed of: a pump cylinder 73 disposed in the liquid cylinder 8 and / or in an extension of the cylinder 8; and a pump piston 74 movable by a hydraulic piston 10 and / or the liquid cylinder 8, the pump piston being capable of translation within the pump cylinder 73.

[0225] It should be noted that pump cylinder 73 can be directly or indirectly fixed to liquid cylinder 8, or fixed to gas and liquid reservoir 14, or fixed to hydraulic piston 10, and the same applies to pump piston 74.

[0226] It is important to note, especially Figures 10 to 16 As a non-limiting example, the liquid spray pump 72 may include at least one pump inlet vane 79 and at least one pump depressurization vane 80, the vanes 79 and 80 being able to be fixed to the pump cylinder 73 or the pump piston 74.

[0227] It may also be noted that the pump cylinder 73 may include a discharge port along its length, which allows the pressure relief of the liquid spray pump 72 on the working liquid 13 to be increased or decreased depending on the relative position of the pump piston 74 in the pump cylinder 73.

[0228] exist Figures 10 to 12 It should be noted that the pump piston 74 may include a stroke start contact pin 77, which moves the pump piston by means of the stroke start contact pin, and the piston 74 returns to the stroke end abutment part 78 by means of the piston return mass 76 or the piston return spring (not shown).

[0229] This particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention makes it possible for the stroke of the pump piston 74 to be shorter than that of the hydraulic piston 10, and for example, the liquid spray nozzle 71 atomizes the working liquid 13 in the internal volume of the gas and liquid reservoir 14 only when the hydraulic piston 10 reaches a position close to its high neutral position.

[0230] exist Figures 13 to 16 As shown in the diagram, the pump piston 74 can be moved by means of a movable spring 81, which enables the change in distance between the pump piston 74 and the pump cylinder 73 to be separated from the change in distance between the liquid cylinder 8 and the hydraulic piston 10.

[0231] This particular configuration can also be maintained to keep a relatively constant pressure in the pump cylinder 73, regardless of the rotational speed of the crankshaft 24.

[0232] exist Figure 3 , Figure 6 and Figure 7 China and in Figures 17 to 21As shown in the diagram, with each rotation of crankshaft 24, overflow pump 82 can transfer a small amount of working fluid 13 from overflow reservoir 83 to gas and liquid reservoir 14 and / or liquid cylinder 8.

[0233] Therefore, when the hydraulic piston 10 performs reciprocating motion in the liquid cylinder 8 and when the variable hydraulic volume 12 is at its minimum, the gas and liquid reservoir 14 is completely filled with working fluid 13. A small amount of working fluid 13 introduced into the gas and liquid reservoir 14 by the overflow pump 82 overflows with each rotation of the crankshaft 24 of the reservoir 14 to return to the overflow reservoir 83 via the outlet port 7 and the pressure relief chamber 62.

[0234] This particular configuration of the mechanical-liquid piston slow-expansion compressor 1 according to the invention allows all the working gas 5 contained in the variable pneumatic volume 2 to be discharged from the volume 2 when the variable hydraulic volume 12 is at its minimum, which gives the volume 2 an infinite volume ratio and a volumetric efficiency close to 100%.

[0235] like Figure 3 As indicated, the overflow reservoir 83 may be connected to the pressure relief chamber 62, in which the working gas pressure 5 is close to or equal to the working gas pressure in the pressure relief chamber 62, and the reservoir 83 is located below the pressure relief chamber 62, so that the working liquid 13 overflowing from the gas and liquid reservoir 14 via the outlet port 7 and the pressure relief chamber 62 naturally returns to the overflow reservoir 83 due to gravity.

[0236] exist Figures 17 to 21 It should be noted that the overflow pump 82 includes a pump blind cylinder 84, in which the overflow pump piston 85 can be translated in a sealed manner. The overflow pump piston and the cylinder 84 form a variable overflow pump volume 86. When the variable overflow pump volume increases, it is filled with working fluid 13 from the overflow reservoir 83 via at least one overflow pump inlet vane 87. When the variable overflow pump volume decreases, it depressurizes the fluid 13 to the gas and liquid reservoir 14 and / or the liquid cylinder 8 via a pressure relief valve 88.

[0237] It should be noted that the pump blind cylinder 84 may be assembled or not assembled; that is, it may be made from a single part or it may receive a cylinder head that closes the end of the pump blind cylinder opposite the end blocked by the overflow pump piston 85.

[0238] exist Figures 17 to 19It should be noted that the overflow pump piston 85 can be a double-body staged piston 89. This double-body staged piston includes a large-diameter body 93 having a surface 90 with a large cross-section forming one of the walls of the variable overflow pump volume 86. The staged piston 89 also includes a small-diameter body 94 axially opposite to the surface 90 with the large cross-section. This small-diameter body is hermetically translatable within an actuating cylinder 92, the internal volume of which is directly or not directly connected to the internal volume of the liquid cylinder 8. The small-diameter body 94 includes a surface 91 with a small cross-section. Pressure in the liquid cylinder 8 is applied to this surface. On the surface with a small cross-section, the staged piston 89 also provides a surface 95 with an average cross-section at the junction between the large-diameter body 93 and the small-diameter body 94. The small-diameter body 94 protrudes from this surface with an average cross-section, which is connected to the overflow reservoir 83 and is subjected to pressure in the reservoir 83. The staged piston abutment portion 117 fixes the maximum volume of the variable overflow pump volume 86, and the double-body piston return spring 96 tends to push against the double-body staged piston 89 in the direction of the surface 90 with a large cross-section.

[0239] exist Figures 17 to 19 It should also be noted that the pressure relief valve 88 includes a valve actuator piston 97, which is hermetically translatable within a valve actuator cylinder 98. This valve actuator piston first has a valve actuation axial surface 99, which communicates with an overflow reservoir 83. Pressure in the reservoir 83 is applied to this valve actuation axial surface. When the valve actuator piston 97 moves in the direction of this surface 99, the surface 99 enables the overflow vanes 100 of the overflow vane seat 104 to rise. This has the effect of allowing the variable overflow pump volume 86 to communicate via the overflow vanes 100 with the gas and liquid reservoir 14 and / or the liquid cylinder 8. Furthermore, the valve actuator piston secondly has a liquid cylinder-side axial surface 1... 02, the axial surface of the liquid cylinder side is connected to the liquid cylinder 8 or the gas and liquid reservoir 14. The pressure in the cylinder 8 is applied to the axial surface of the liquid cylinder side, and when the valve actuator piston 97 moves in the direction of the axial surface of the liquid cylinder side 102, the axial surface of the liquid cylinder side can contact the liquid cylinder side abutment 118. However, the actuator piston return spring 103 tends to push the valve actuator piston in the direction of the valve actuator piston 97 valve actuator axial surface 99, and the overflow vane return spring 128 tends to cause the overflow vane 100 to return to contact the overflow vane seat 104 it engages with. The force generated by the actuator piston return spring 103 is greater than the force generated by the overflow vane return spring 128.

[0240] As an alternative not shown, the pressure relief valve 88 may include a cylindrical slider with a slider recess on its outer surface. The slider is capable of hermetically translating within a slider cylinder. An intake space leads to this slider cylinder, which is connected to a variable overflow pump volume 86. An exhaust space is connected to a gas and liquid reservoir 14 or to a liquid cylinder 8. Depending on the axial position of the cylindrical slider within the slider cylinder, the slider recess may connect or not connect the intake space and the exhaust space. The cylindrical slider 97 has a reservoir-side axial surface and a liquid cylinder-side axial surface, the reservoir-side axial surface communicating with an overflow reservoir 83. The pressure in the reservoir 83 is applied to the reservoir-side axial surface, which can rest on the liquid cylinder-side sliding member abutment. The liquid cylinder-side axial surface is in communication with the liquid cylinder 8 or the gas and liquid reservoir 14, and the pressure in the cylinder 8 or the gas and liquid reservoir 14 is applied to the liquid cylinder-side axial surface. However, the sliding member return spring tends to push the cylindrical sliding member against the reservoir-side axial surface in the direction of the cylindrical sliding member until it reaches the reservoir-side sliding member abutment. When the sliding member reaches the reservoir-side sliding member abutment, the reservoir-side sliding member abutment makes the air intake space communicate with the exhaust space through the sliding member recess.

[0241] exist Figure 20 and Figure 21 As shown, the overflow pump piston 85 can be a double-body staged piston 89, which includes a large-diameter body 93 having a large cross-sectional surface 90 connected to and subjected to pressure in the overflow reservoir 83. The staged piston 89 also includes a small-diameter body 94 axially opposite to the large cross-sectional surface 90, which is hermetically translatable within an actuating cylinder 92 whose internal volume is directly or indirectly connected to the internal volume of the liquid cylinder 8. The small-diameter body 94 includes a surface 91 with a small cross-section. The pressure in the liquid cylinder 8 is applied to the surface with a small cross-section. The staged piston 89 also provides a surface 95 with an average cross-section at the junction between the large-diameter body 93 and the small-diameter body 94. The small-diameter body 94 protrudes from the surface with an average cross-section. The surface 95 forms one of the walls of the variable overflow pump volume 86. The staged piston abutment portion 117 fixes the maximum volume of the variable overflow pump volume 86, and the double-body piston return spring 96 tends to push against the double-body staged piston in the direction of the surface 91 with a small cross-section of the double-body staged piston 89.

[0242] Still in Figure 20 and Figure 21As shown, the pressure relief valve 88 may include a valve actuator piston 97 that is hermetically translatable within a valve actuator cylinder 98. This valve actuator piston first has a valve actuation axial face 99 that communicates with a liquid cylinder 8, and pressure in the cylinder 8 is applied to this valve actuation axial face. When the valve actuator piston 97 moves in the direction of this face 99, the face 99 enables the overflow vanes 100 of the overflow vane seat 104 to rise. This has the effect of allowing the variable overflow pump volume 86 to communicate via the overflow vanes 100 with the gas and liquid reservoir 14 and / or the liquid cylinder 8. The valve actuator piston also has a reservoir-side axial face 10. 1. The axial surface of the reservoir side is connected to the overflow reservoir 83. The pressure in the reservoir 83 is applied to the axial surface of the reservoir side. When the valve actuator piston 97 moves in the direction of the axial surface of the reservoir side 101, the axial surface of the reservoir side can contact the overflow reservoir side abutment 130. However, the actuator piston return spring 103 tends to push the valve actuator piston in the direction of the valve actuator piston 97 valve actuator axial surface 99, and the overflow vane return spring 128 tends to cause the overflow vane 100 to return to contact the overflow vane seat 104 it engages with. The force generated by the actuator piston return spring 103 is greater than the force generated by the overflow vane return spring 128.

[0243] As an alternative not shown, the pressure relief valve 88 may include a cylindrical slider with a slider recess on its outer surface. The slider is translatable within a slider cylinder, connecting to an intake space of the variable overflow pump volume 86 and an exhaust space connected to the gas and liquid reservoir 14 or the liquid cylinder 8. Depending on the axial position of the cylindrical slider within the slider cylinder, the slider recess may connect or not connect the intake space and the exhaust space. The cylindrical slider has an axial surface on the reservoir side and an axial surface on the liquid cylinder side, the reservoir side axial surface resting against the reservoir side slider. On the upper part, the axial surface of the reservoir side is connected to the overflow reservoir 83, and the pressure in the reservoir 83 is applied to the axial surface of the reservoir side. The axial surface of the liquid cylinder side is connected to the liquid cylinder 8 or the gas and liquid reservoir 14, and the pressure in the cylinder 8 is applied to the axial surface of the liquid cylinder side. However, the sliding member return spring tends to push the cylindrical sliding member against the direction of the axial surface of the liquid cylinder side of the cylindrical sliding member until it reaches the sliding member abutment portion of the liquid cylinder side. When the sliding member reaches the sliding member abutment portion of the liquid cylinder side, the sliding member abutment portion of the liquid cylinder side makes the air intake space connected to the exhaust space through the sliding member recess.

[0244] according to Figure 23In a specific embodiment of the mechanical liquid piston slow expansion compressor 1 according to the invention shown, the balancing member 112 may replace the piston guide member 23 wholly or partially to tilt the liquid cylinder 8 during the rotation of the crankshaft 24 in order to reduce or even eliminate the radial force exerted on the guide member 23 by the tilt of the cylinder due to the mass of the cylinder 8 and the gravity of the earth.

[0245] According to this specific configuration, the balancing member 112 can be composed of a balancing mast 113, which includes a balancing mass 116 on one hand, and articulates about a mast axis 114 that is parallel to the inclined axis 9 of the liquid cylinder 8 and fixed to the static frame 40 on the other hand. However, the balancing mast 113 forms a pivot-sliding joint motion part 115 with the cylinder 8 and constitutes an imbalance opposite to the imbalance of the cylinder 8. The pivot-sliding joint motion part 115 can be as follows: Figure 23 The shaft shown is formed by protruding from the outer surface of the liquid cylinder 8, and the shaft receives a bearing that can move within an elliptical cavity of the balancing mast 113.

[0246] It should be noted that, according to a specific embodiment of the mechanical liquid piston slow expansion compressor 1 according to the present invention, the balancing mast 113 may receive a balancing mass 116, the weight and / or position of which may be variable.

[0247] It should be noted that, as an alternative to the above, the balancing member 112 may be composed of any type of rotary drive and synchronization mechanism of the liquid cylinder 8 or a mechanism with an elastic connection, which itself tends to reduce or even eliminate the radial force applied to the piston guide member 23 by the tilt of the cylinder due to the mass of the cylinder 8 and the gravity of the earth. Operation of the present invention

[0248] Given Figures 1 to 23 The operation of the mechanical liquid piston slow expansion compressor 1 according to the present invention can be easily understood.

[0249] The purpose of the expansion compressor 1 is specifically to form a variable pneumatic volume 2 in which heat exchange between the working gas 5 (which may be atmospheric air) and the working liquid 13 (which may be water) is maximized during compression or expansion, and this makes the compression or expansion as isothermal as possible, with the working liquid 13 having a high volumetric heat capacity primarily applying its temperature to the working gas 5, which has a low volumetric heat capacity.

[0250] Therefore, as Figures 1 to 4 , Figures 10 to 12 as well as Figure 22 and Figure 23As shown, when the mechanical liquid piston type slow expansion compressor 1 according to the present invention forms the compressor 3, the working gas 5 is compressed in the variable pneumatic volume 2.

[0251] In this case, the pressure and temperature of the gas 5 first rise until the temperature reaches the temperature of the working liquid 13 contained in the liquid cylinder 8 and the gas and liquid reservoir 14. After reaching this temperature level, the gas 5 continues to be compressed and its pressure rises. However, the heat generated by the compression of the gas 5 is transferred to the liquid 13 as the heat is generated, so that the compression of the gas 5 ends almost isothermally.

[0252] On the contrary, and as Figures 13 to 16 As shown, if the mechanical liquid piston type slow expansion compressor 1 according to the present invention forms an expander 4, the working gas 5 expands in the variable pneumatic volume 2.

[0253] In another scenario, the pressure and temperature of the gas 5 are initially reduced until the temperature reaches the temperature of the working liquid 13 contained in the liquid cylinder 8 and the gas and liquid reservoir 14. After reaching this temperature level, the gas 5 continues to expand and its pressure decreases, however, its temperature is persistently maintained close to the temperature of the working liquid 13, which for this purpose transfers heat to the gas 5, such that the expansion of the gas 5 ends nearly isothermally.

[0254] Therefore, and as Figures 1 to 4 , Figures 10 to 12 , Figure 22 and Figure 23 as well as Figures 13 to 16 As shown, the mechanical liquid reciprocating slow expansion compressor 1 according to the invention can be configured as a compressor 3 or an expander 4, in which a gas and liquid reservoir 14 with a variable pneumatic volume 2 is formed to house a heat exchange and accumulation member 16, which is provided to exchange heat with the working gas 5 or with the working liquid 13, and before the heat is discharged to the heating member 18 via a heat discharge or input member 17 (e.g. Figure 9 (as shown) or after the heat has been introduced from the cooling member 19 via the output or input member 17 (also as shown) Figure 9 (As shown) Temporarily store all or part of the heat.

[0255] like Figure 9 As shown, and as a non-limiting example, the heating element 18 may be constituted by an underfloor heating and cooling device 106 installed in the building 121, while the cooling element 19 may take the form of an air-water exchanger 107 placed on the exterior 122 of the building 121.

[0256] In addition to facilitating heat exchange between the working gas 5 and the working liquid 13 during compression or expansion, the mechanical liquid piston slow expansion compressor 1 according to the invention also minimizes energy loss caused by friction, which is undesirable because friction reduces the efficiency of the compressor 3 or expander 4 formed by the expansion compressor 1.

[0257] Therefore, in contrast to the conventional rod and crank systems included in commercially available compressors and alternative thermal motors, the hydraulic piston 10 of the mechanical liquid piston slow expansion compressor 1 according to the invention is sealed and translated within a liquid cylinder 8 to form a variable hydraulic volume 12 with the liquid cylinder, which is not subjected to significantly high radial forces.

[0258] For example in Figure 1 and Figure 2 As can be seen, due to the pivoting of the liquid cylinder 8 about the inclined axis 9 which is perpendicular to the axis of the cylinder 8 and fixed to the static frame 40, the hydraulic piston 10 and its connecting rod 11 are kept parallel to the cylinder 8 by the piston guide member 23 fixed to the liquid cylinder 8, regardless of the position of the piston 10 in the cylinder 8, thus achieving this result.

[0259] As in Figures 1 to 3 In China Figures 6 to 8 In China Figures 10 to 16 China and in Figure 22 and Figure 23 As can be seen, the piston guide member 23 may be composed of a sliding pivot connection 47, which is formed between the outer cylindrical surface 48 of the connecting rod 11 and the sliding ring 49 that is fixedly connected to the liquid cylinder 8 by means of the annular carrier structure 50.

[0260] Therefore, and as Figure 1 and Figure 2 , Figures 6 to 8 as well as Figure 22 and Figure 23 As shown, the crank 26 is always approximately held on the axis of the liquid cylinder 8, and the second rod end 30 of the connecting rod 11 performs joint movement around the crank.

[0261] According to this particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention, unlike the most common rod and crank system, the axial force exerted by the pressure of the working gas 5 on the hydraulic piston 10 by means of the working fluid 13 is no longer converted from a radial force other than the radial force exerted by the piston 10 on the liquid cylinder 8.

[0262] In fact, the low rotational speed of the mechanical liquid piston slow expansion compressor 1 is not conducive to establishing a hydrodynamic lubrication system between the hydraulic piston 10 and the liquid cylinder 8, which requires a high relative velocity between the piston 10 and the cylinder 8.

[0263] Furthermore, if the working fluid interfering between the hydraulic piston 10 and the liquid cylinder 8 is water, which is not very viscous and has low lubrication properties, it is also disadvantageous to establish a hydrodynamic load-bearing system at the interface between the piston 10 and the cylinder 8.

[0264] This particular characteristic of the mechanical liquid piston slow expansion compressor 1 (which includes removing any radial force exerted by the hydraulic piston 10 on the liquid cylinder 8) is of utmost importance, especially giving any heat pump 55 formed by the compressor 3 and expander 4 according to the invention a higher efficiency and coefficient of performance than conventional heat pumps that operate on refrigerant fluid.

[0265] The goal is always to minimize energy loss caused by friction. Figures 1 to 3 In China Figures 6 to 8 China and in Figure 22 and Figure 23 It should be noted that all pivot connections of the mechanical liquid reciprocating slow expansion compressor 1 accept roller bearings 105 known in themselves, whether this is related to the tilting shaft 9, the shaft bearing 25 or the crank 26.

[0266] The actual coefficient of friction of the roller bearing 105 is very low, the pivot connection dissipates very little energy, and has a very small negative impact on the energy efficiency of any heat pump 55 constituted by the mechanical liquid piston slow expansion compressor 1 according to the invention.

[0267] The objective of the mechanical liquid piston slow expansion compressor 1 according to the present invention is also to minimize energy loss caused by working gas leakage 5, which reduces the actual efficiency of the compressor 3 or expander 4 formed by the expansion compressor 1.

[0268] In this regard, it should be noted that the hydraulic piston 10 forms a seal with the liquid cylinder 8 in which it translates, and this seal is applied to the working liquid 13, rather than the working gas 5 itself, which is always kept above the working liquid 13 due to its low density, gravity, and the low rotational speed of the mechanical liquid piston slow expansion compressor 1.

[0269] This particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention results in a seal formed by the hydraulic piston 10 and the liquid cylinder 8 that prevents leakage of the working liquid 13 but not the working gas 5, the volumetric flow rate of which the possible leakage is highly limited by the high density and viscosity of the liquid 13 (in this case, and as a non-limiting example, water).

[0270] It should also be noted that achieving a complete seal between the hydraulic piston 10 and the liquid cylinder 8 is more achievable than the slow rotation of the mechanical liquid piston type slow expansion compressor 1.

[0271] In fact, the low rotational speed of the expansion compressor 1 means a low relative linear speed between the hydraulic piston 10 and the liquid cylinder 8, which makes it possible to equip the hydraulic piston 10 with a flexible and continuous seal 51, which consists, for example, an elastomeric O-ring that is tightly attached to the inner wall of the liquid cylinder 8, or a friction ring made of polytetrafluoroethylene (a material that is particularly wear-resistant) filled with anti-friction particles.

[0272] Advantageously, it should be noted that the working fluid 13 may be formed from a mixture of ethylene glycol and water, which, in addition to lowering the freezing temperature of the water and preventing it from freezing, can contribute to increased durability of the seal 51, limit energy loss caused by friction generated by the seal 51, and, if necessary, reduce possible leakage of the working fluid 13 at the contact interface between the hydraulic piston 10 and the liquid cylinder 8.

[0273] Note that in order to keep the working fluid 13 in complete contact with the hydraulic piston 10 at all times, and to prevent cavitation or excessive mixing between the working gas 5 and the working fluid 13, the maximum acceleration or deceleration of the hydraulic piston 10 between its midpoint and its neutral position must be less than the Earth's gravity.

[0274] In this respect, the rotational speed of crankshaft 24 must be kept low, and as a non-limiting example, it will be fixed at forty revolutions per minute.

[0275] This low speed explains the necessity of adding the kinetic energy storage component 28 to the crankshaft 24, according to Figure 1 and Figure 2 , Figures 6 to 8 as well as Figure 22 and Figure 23The example shown is of an embodiment of the mechanical liquid piston slow expansion compressor 1 according to the present invention, in which the kinetic energy storage component is composed of a low-speed inertial flywheel 66, which is rotatably fixed to a crankshaft 24 on one hand and rotatably fixed to a gear 67 on the other hand. The drive motor 27 rotates the gear by means of a high-efficiency annular drive pinion 68, the base circle diameter of which is smaller than the base circle diameter of the ring 67. The ring and the pinion 68 form a high transmission ratio meshing system 69.

[0276] exist Figure 6 It should also be noted that the high-speed inertial flywheel 70 can be advantageously configured to be rotatably fixed to the annular drive pinion 68.

[0277] According to this particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention, the instantaneous torque change applied to the crankshaft 24 by the compression or expansion of the working gas 5 in the gas and liquid reservoir 14 is mainly absorbed by the inertia of the low-speed inertial flywheel 66 and the inertia of the high-speed inertial flywheel 70, so that the torque resisting or driving the drive motor 27 is smooth, and the motor 27 is therefore mainly subjected to the average resistance torque necessary to maintain the regular rotation of the crankshaft 24.

[0278] In addition to avoiding any cavitation or over-mixing between the working gas 5 and the working liquid 13, the low rotational speed of forty revolutions per minute applied to the crankshaft 24 allows ample time for the working gas 5 to be transferred to the filling component 20 or the discharge component 22 of the compressor 3 and the expander 4.

[0279] In fact, apart from allowing time for heat exchange to occur in the gas and liquid reservoir 14 between the working gas 5 and / or working liquid 13 on the one hand and the heat exchange and accumulation component 16 on the other hand, the slow rotation of the compressor 3 or the expander 4 has the advantage of allowing time for the transfer of the working gas 5 in order to limit pressure loss at the inlet port 6 and outlet port 7 of the compressor 3 or the expander 4.

[0280] In practice, the discharge member 22 that allows or prohibits the transmission of working gas 5 from the intake chamber 21 to the filling member 20 of the gas and liquid reservoir 14 via the inlet port 6, or allows or prohibits the transmission of working gas 5 from the gas and liquid reservoir 14 to the pressure relief chamber 62 via the outlet port 7, may be composed of at least one compressor vane 52, which may or may not be assisted by an electric component, at least one controlled compressor valve 53, or at least one controlled expander valve 54.

[0281] However, these components 52, 53, 54 resist the inertial force of their movement, the strength of which varies with the square of the rotational speed of the crankshaft 24, and in this respect, if the shaft 24 rotates only forty revolutions per minute, for example, the force is so low that it no longer has a negative impact on the efficiency of the mechanical liquid piston slow expansion compressor 1 according to the invention.

[0282] As can be seen from the above, the actual pressure-volume thermodynamic diagram of the heat pump 55, including the compressor 3 and expander 4 formed by the mechanical liquid piston slow expansion compressor 1 according to the present invention, is as close as possible to the pressure-volume thermodynamic diagram of the ideal Carnot cycle, and the practice is as close as possible to the theory.

[0283] The low rotational speed of the crankshaft 24 also gives the mechanical liquid piston slow expansion compressor 1 according to the invention a service life of decades or even centuries, although this requires the replacement of a few aging parts, such as the seal 51 of the hydraulic piston 10.

[0284] To continue describing the invention as follows Figures 6 to 9 The operation of the mechanical liquid reciprocating slow expansion compressor 1 shown is, in this case, assumed to be that the compressor 3 and expander 4 formed by the slow expansion compressor 1 are coupled to form a heat pump 55, which performs a refrigerant cycle close to the ideal Carnot cycle.

[0285] In this regard, Figures 6 to 9 It should be noted that the pressure relief chamber 62 of the compressor 3 is connected to the intake chamber 21 of the expander 4 through a high-pressure gas conduit 56, so that the working gas 5 depressurized through the pressure relief chamber 62 of the compressor 3 is introduced into the expander 4 through the intake chamber 21 of the expander 4, and the crankshaft 24 of the compressor 3 is connected to the crankshaft 24 of the expander 4.

[0286] exist Figure 9 Note that the high-pressure gas conduit 56 is connected to the high-pressure gas reservoir 58, which, as a non-limiting example, can store working gas 5 at a temperature of forty degrees Celsius and a pressure of forty-six bar.

[0287] In this respect, and as Figure 9 As shown, the high-pressure gas conduit 56 and the high-pressure gas reservoir 58 may be advantageously coated with a thermal insulation layer 59, which prevents any useless heat dissipation to the external environment of the heat pump 55.

[0288] exist Figure 9It should also be noted that the intake chamber 21 of the compressor 3 and the pressure relief chamber 62 of the expander 4 are connected by a low-pressure gas reservoir 60. The intake chamber and the pressure relief chamber are respectively connected to the low-pressure gas reservoir through a low-pressure gas conduit 61.

[0289] As a non-limiting example, the working gas 5 contained in the low-pressure gas reservoir 60 has a pressure of 1.5 bar absolute and a temperature of 2 degrees Celsius.

[0290] Still as a non-restrictive example and as Figure 9 As shown, in this case, it is assumed that the heating element 18 is composed of an underfloor heating and cooling device 106 in which a heat transfer fluid 37 circulates, transferring heat from the compressor 3 to the underfloor device 106. The fluid 37 enters the underfloor device 106 at a temperature of thirty-five degrees Celsius, so that the underfloor device maintains a temperature of twenty-one degrees Celsius in the residential building 121. The cooling element 19 is formed by an air-water exchanger 107, which is placed outside the building 121 at 122, and atmospheric air is forced through the air-water exchanger by two electric fans 108. The heat transfer fluid 37 circulates in the exchanger 107 to transfer heat from the exchanger 107 to the expander 4. The fluid 37 enters the exchanger 107 at a temperature of two degrees Celsius, while the external temperature of the building 121 is seven degrees Celsius.

[0291] about Figures 6 to 8 Furthermore, it is assumed that the stroke of the hydraulic piston 10 of the compressor 3 and the expander 4 is 400 mm, and the cylinder diameter of the liquid cylinder 8 of the compressor 3 and the expander 4 is 410 mm, so the piston 10 and the cylinder 8 thus form a variable hydraulic volume 12 of 51.5 liters.

[0292] Figure 5 The main pressure-volume diagram is shown, not necessarily to scale, such as the one performed by the heat pump 55 just described, the top diagram performed by the compressor 3, and the bottom diagram performed by the expander 4. The two diagrams are virtually connected by dashed arrows to reconstruct the diagram of the heat pump Carnot cycle.

[0293] The diagram regarding compressor 3, namely, Figure 5 The top view shows that the cross section AB forms an adiabatic compression, which enables the initial temperature T1 of the working gas 5 to be increased from two degrees Celsius to forty degrees Celsius, with forty degrees Celsius denoted as T2.

[0294] When this is done, the pressure of working gas 5 changes from 1.5 bar to 2.4 bar.

[0295] The hydraulic piston 10 of the compressor 3 continues its stroke to its high neutral position, and the cross section BC forms isothermal compression. During this period, the pressure of the working gas 5 changes from 2.4 bar to 46 bar, while the temperature T2 of the gas 5 remains constant at 40 degrees Celsius. The gas 5 transfers the heat to the working liquid 13 and the heat exchange and accumulation component 16 when heat Q1 is generated.

[0296] Cross section CD corresponds to the transfer of working gas 5 from the gas and liquid storage tank 14 of compressor 3 to... Figure 9 The high-pressure gas storage device 58 shown has a gas 5 with a temperature of 40 degrees Celsius and a pressure of 46 bar.

[0297] The transmission occurs continuously via the compressor vanes 52 of the compressor 3, its pressure relief chamber 62, and the high-pressure gas conduit 56 at the outlet port 7 of the compressor 3.

[0298] The cross-section DE of the diagram of compressor 3 illustrates a sudden drop in pressure in the gas and liquid reservoir 14 of compressor 3 when compressor vanes 52 at outlet port 7 of compressor 3 are closed and compressor vanes 52 at inlet port 6 of compressor 3 are immediately opened.

[0299] Cross section EA corresponds to the compressor vanes 52 of the compressor 3 continuously supplying gas from the compressor via the low-pressure gas conduit 61, the inlet chamber 21, and the inlet port 6 of the compressor 3. Figure 9 The working gas 5 is drawn into the low-pressure gas reservoir 60 shown.

[0300] The diagram of expander 4, i.e. Figure 5 The bottom view shows that the cross section FG corresponds to the transfer of working gas 5 from high-pressure gas reservoir 58 to gas and liquid reservoir 14 of expander 4, where the temperature T2 and pressure of gas 5 are 40 degrees Celsius and 46 bar, respectively.

[0301] The cross section GH forms an adiabatic expansion, which reduces the initial temperature T2 of the working gas 5 from forty degrees Celsius to two degrees Celsius, which is denoted as T1. However, at the same time, the pressure changes from forty-six bar to about twenty-nine bar.

[0302] Then, the cross section HI undergoes isothermal expansion, during which the pressure of the working gas 5 changes from 29 bar to 1.5 bar absolute value. However, the temperature T1 of the gas 5 remains constant at 2 degrees Celsius. The gas removes heat Q2 at the working liquid 13 and at the heat exchange and accumulation member 16 to keep its temperature close to 2 degrees Celsius.

[0303] Figure 5The cross section IJ corresponds to the depressurization of the working gas 5 contained in the gas and liquid reservoir 14 of the expander 4 to the low-pressure gas reservoir 60. The gas 5 is continuously circulated to the low-pressure gas reservoir 60 via the controlled expander valve 54 of the discharge member 22 forming the outlet port 7 of the expander 4, then via the depressurization chamber 62 of the expander 4, and finally via the low-pressure gas conduit 61 connecting the expander 4 to the low-pressure gas reservoir 60.

[0304] The cross-section of the pressure-volume diagram of the expander 4 itself illustrates a sudden increase in pressure in the gas and liquid reservoir 14 of the expander 4 when the controlled expander valve 54 of the discharge member 22 forming the outlet port 7 of the expander 4 is closed; however, immediately thereafter, the controlled expander valve 54 of the filling member 20 forming the inlet port 6 of the expander 4 opens to participate in a new cycle of the expander 4.

[0305] therefore, Figure 5 The two pressure-volume diagrams shown are used in conjunction to reconstruct the Carnot cycle of the heat pump using working gas 5, whose state remains unchanged. Compressor 3 performs the hot part of the cycle, while expander 4 performs the cold part.

[0306] If the output of heat Q1 and heat Q2 is perfect, then the heating power of the heat pump 55 just described will be approximately seventeen kilowatts for a coefficient of performance greater than eight.

[0307] Once the losses caused by friction at different pivot connections are deducted (e.g.) Figures 1 to 3 , Figures 6 to 8 as well as Figure 22 and Figure 23 As shown, these pivot connections are made of low-friction roller bearings 105, and the coefficient of performance of the heat pump 55 drops to approximately 7.7.

[0308] If the cooling component 19 is made of, for example Figure 9 The air-water exchanger 107 shown is configured such that the cumulative power consumed by the electric fan 108 to force heat exchange between atmospheric air and water circulating in the exchanger 107 is 500 watts, and the coefficient of performance of the heat pump 55 drops to 6.3.

[0309] From these observations, it is understood that any benefit of the specific mechanical configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention is to be understood that, in fact, if all conditions are the same, the expansion compressor 1 with a conventional connecting rod engaged with a stationary liquid cylinder, even with a rod / crank ratio of four, i.e. a particularly bulky rod of 840 mm in length, would result in a heat pump coefficient of performance of about four, rather than the 6.3 achievable with the specific mechanical configuration of the slow expansion compressor 1 according to the invention.

[0310] The difference in performance coefficient between such a heat pump and that of a conventional heat pump would not be sufficient to justify the technological change. Moreover, such Carnot cycle heat pumps using gases without phase change are very likely to be much heavier, larger, and bulkier than their conventional counterparts.

[0311] The only benefit of replacing refrigerant fluids such as hydrofluorocarbons with atmospheric air is insufficient to justify the technological change, since carbon dioxide, which will be provided as a substitute for said fluids in the near future, will still be environmentally acceptable.

[0312] However, the current achievable performance coefficient of approximately six instead of four represents a 33 percent energy saving while providing the same service, which is very interesting in terms of both energy and economic levels as well as environmental levels.

[0313] However, this performance coefficient is only Figure 5 The heat exchange Q1 and Q2 shown on the pressure-volume diagram can only be achieved using the mechanical liquid piston slow expansion compressor 1 according to the present invention under conditions of high efficiency.

[0314] Therefore, in Figures 1 to 4 In China Figure 8 and Figure 9 China and in Figure 17 As shown, the heat exchanger conduit 36 ​​housed in the gas and liquid reservoir 14 of the compressor 3 and the expander 4 can be formed, for example, by a copper coil 109 in which the heat transfer fluid 37 circulates, and the heat exchanger conduit constitutes the heat exchange and accumulation component 16 and the heat outlet and intake component 17.

[0315] According to this particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention, the heat exchanger conduit 36 ​​absorbs or transfers heat to the working liquid 13 and the working gas 5, and then the heat transfer fluid 37 circulating in the conduit 36 ​​transfers the heat from the cooling member 19 or to the heating member 18.

[0316] exist Figure 3 and Figure 4 It should be noted that the coils formed by the copper coil 109 are maintained in a proper abutting position by the partition baffle 110. External fins may optionally be added to the copper coil, which increases the contact surface between the heat exchanger duct 36 and the working liquid 13 or working gas 5.

[0317] Moreover, when the hydraulic piston 10 is positioned in its low neutral position and when the variable pneumatic volume 2 is at its maximum, the working gas 5 is exposed to contact with the copper coil 109 and its optional external fins; however, when the piston 10 is positioned in its high neutral position and when the variable pneumatic volume 2 is at its minimum, the coil 109 is immersed in the working fluid 13.

[0318] exist Figures 1 to 4 In China Figure 8 China and in Figures 10 to 16 As shown, the upper portion of the gas and liquid reservoir 14 receives a liquid spray nozzle 71, which atomizes the working liquid 13 into fine droplets within the internal volume of the reservoir 14, causing the liquid 13 to form an additional heat exchange and accumulation member 16, which removes or transfers heat to the working gas 5, particularly in relation to... Figure 5 The isothermal compression phase of the pressure-volume diagram with respect to the cross section BC of the compressor 3, and the expansion phase of the diagram with respect to the cross section HI of the expander 4.

[0319] This particular configuration of the mechanical-liquid piston slow-expansion compressor 1 according to the present invention enables the maximization of heat exchange between the working gas 5 and the working liquid 13.

[0320] like Figures 2 to 4 , Figure 8 as well as Figures 10 to 16 As indicated, the liquid spray nozzle 71 is supplied with working liquid 13 by a liquid spray pump 72, which is composed of a pump cylinder 73 that houses a pump piston 74 that is moved by a hydraulic piston 10.

[0321] According to a specific embodiment of the liquid spray pump 72, the operation of the compressor 3 and the pump 72 is as follows: Figures 10 to 12 The details are as follows, and the operation of the expander 4 according to a specific embodiment of the liquid spray pump 72 is described in Figures 13 to 16 As detailed in the figures, the details of the operation will be clear to those skilled in the art.

[0322] exist Figure 3 , Figure 6 and Figure 7 It should be noted that the pressure relief chamber 62 of the compressor 3 and expander 4 formed by the mechanical liquid piston slow expansion compressor 1 according to the present invention is connected to the overflow reservoir 83, the lower part of which includes the overflow pump 82.

[0323] According to this particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention, with each rotation of the crankshaft 24, the overflow pump 82 transfers a small amount of working fluid 13 from the overflow reservoir 83 to the liquid cylinder 8 of the compressor 3, or, depending on the situation, to the liquid cylinder of the expander 4.

[0324] The specific configuration allows the gas and liquid reservoir 14 to be fully filled with working fluid 13 when the hydraulic piston 10 performs reciprocating motion in the liquid cylinder 8 and when the variable hydraulic volume 12 is at its minimum. A small amount of working fluid 13 introduced into the gas and liquid reservoir 14 by the overflow pump 82 overflows with each rotation of the crankshaft 24 of the reservoir 14 to return to the overflow reservoir 83 via the outlet port 7 and the pressure relief chamber 62.

[0325] This particular embodiment of the mechanical-liquid piston slow-expansion compressor 1 according to the invention enables all the working gas 5 contained in the variable pneumatic volume 2 to be effectively discharged from the volume 2 when the variable hydraulic volume 12 is at its minimum, which gives the variable pneumatic volume 2 an infinite volume ratio and a volumetric efficiency close to 100%.

[0326] As from Figure 3 , Figure 6 and Figure 7 It can be easily deduced that, whether this relates to compressor 3 or expander 4, the working gas pressure 5 in overflow reservoir 83 is similar to the working gas pressure in pressure relief chamber 62.

[0327] exist Figure 3 , Figure 6 and Figure 7 As can be seen, the overflow reservoir 83 is located below the pressure relief chamber 62, so that due to the Earth's gravity, the gas overflowing through the outlet port 7 and the working liquid 13 of the liquid reservoir 14 naturally returns to the overflow reservoir 83.

[0328] Figures 17 to 19 The overflow pump 82 has been shown so that a particular configuration of the mechanical liquid piston slow expansion compressor 1 according to the invention can provide an overflow pump for the compressor 3.

[0329] As stated in Figures 17 to 19 As seen in the image, the overflow pump piston 85 is a double-body staged piston 89, which includes a large-diameter body 93, which includes a surface 90 with a large cross-section, which forms one of the walls of the variable overflow pump volume 86.

[0330] Figures 17 to 19The staged piston 89 is shown to also include a small-diameter body 94 axially opposite a face 90 having a large cross-section. This small-diameter body is hermetically translatable within an actuating cylinder 92, the internal volume of which is connected to the internal volumes of the gas and liquid reservoir 14 and the liquid cylinder 8. The small-diameter body 94 includes a face 91 having a small cross-section, on which pressure in the cylinder 8 is applied. Figure 18 and Figure 19 It is marked as P2.

[0331] exist Figures 17 to 19 Furthermore, it should be noted that the staged piston 89 includes a surface 95 with an average cross-section at the junction between the large-diameter body 93 and the small-diameter body 94. The small-diameter body 94 protrudes from this surface with an average cross-section. The surface 95 is connected to the overflow reservoir 83 and is subjected to the pressure within the reservoir 83. Figure 18 and Figure 19 The middle part is marked as P1, and the stage piston abutment part 117 fixes the maximum volume of the variable overflow pump volume 86, and the double-body piston return spring 96 tends to push the double-body stage piston 89 in the direction of the surface 90 with a large cross section.

[0332] Therefore, and as from Figure 18 It is easy to understand that when the pressure P2 in the liquid cylinder 8 is less than the pressure P1 in the overflow reservoir 83, the double-body stage piston 89 remains in close contact with the stage piston abutment portion 117, while the double-body piston return spring 96 is compressed by the force generated by the pressure difference (P1 minus P2), which is applied to the entire surface of the face 91 with a small cross-section, and the pressure relief valve 88 is closed.

[0333] When the hydraulic piston 10 of compressor 3 reaches the high neutral position, the pressure P2 in liquid cylinder 8 becomes substantially equal to the pressure P1 in overflow reservoir 83, and there is no longer a force applied to the surface 91 with a small cross-section, and as... Figure 19 As shown, the double-body piston return spring 96 pushes against the double-body staged piston 89, which has the effect of discharging the working fluid 13 from the variable overflow pump volume 86 to the liquid cylinder 8 via the open pressure relief valve 88. The actual energy consumption for transferring the fluid 13 from the volume 86 to the cylinder 8 is very low.

[0334] When the hydraulic piston 10 of compressor 3 begins to descend again (this corresponds to...) Figure 5 When the pressure-volume diagram (cross section DE) is used, it is calculated that the pressure relief valve 88 should be closed immediately, and the pressure P2 in the liquid cylinder 8 becomes less than the pressure P1 in the overflow reservoir 83.

[0335] After the twin-body staged piston 89 compresses the twin-body piston return spring 96, the twin-body staged piston moves under the action of the pressure difference (i.e., P1 minus P2) applied to the surface 91 with a small cross-section, while the variable overflow pump volume 86 increases, and the new working fluid 13 load from the overflow reservoir 83 is drawn into the variable overflow pump volume via the overflow pump inlet vane 87.

[0336] like Figure 18 and Figure 19 As shown, the pressure relief valve 88 includes a valve actuator piston 97 that is hermetically translatable within the valve actuator cylinder 98.

[0337] The piston 97 has a valve actuation axial surface 99, which communicates with the overflow reservoir 83, and the pressure P1 in the reservoir 83 is applied to the valve actuation axial surface.

[0338] As in Figure 19 As seen in the diagram, when the valve actuator piston 97 moves in the direction of the axial surface 99, the surface 99 can contact the overflow vane 100 to lift the overflow vane from the overflow vane seat 104.

[0339] In this case, and considering Figure 3 as well as Figure 6 and Figure 7 At a specific location shown, the overflow pump 82 has a variable overflow pump volume 86 connected to the gas and liquid reservoir 14 via the overflow vane 100.

[0340] exist Figure 18 and Figure 19 Furthermore, it should be noted that the valve actuator piston 97 also has a liquid cylinder-side axial surface 102 communicating with the gas and liquid reservoir 14, and the pressure P2 in the reservoir 14 and the liquid cylinder 8 is applied to this liquid cylinder-side axial surface, such as... Figure 18 As shown, when the valve actuator piston 97 moves in the direction of the axial surface 102 on the liquid cylinder side, the surface can contact the liquid cylinder side abutment portion 118.

[0341] exist Figure 18 and Figure 19 It should be noted that the actuation piston return spring 103 tends to push the valve actuator piston 97 against the valve actuator axial surface 99 in the direction of the valve actuator piston 97, and the overflow vane return spring 128 tends to return the overflow vane 100 to contact the overflow vane seat 104 that engages with the overflow vane.

[0342] As from Figure 18 and Figure 19It can be easily deduced that, in order for the pressure relief valve 88 to be operable, the force generated by the actuating piston return spring 103 must be greater than the force generated by the overflow vane return spring 128.

[0343] Therefore, and as from Figure 18 and Figure 19 It is easy to understand that when the pressure P2 in the gas and liquid reservoir 14 and the liquid cylinder 8 is less than the pressure P1 in the overflow reservoir 83, the liquid cylinder side axial surface 102 of the valve actuator piston 97 remains in close contact with the liquid cylinder side abutment portion 118, and the actuator piston return spring 103 is compressed by the force generated by the pressure difference (i.e., P1 minus P2) between the force applied to the valve actuator axial surface 99 and the force applied to the liquid cylinder side axial surface 102.

[0344] In this situation, the overflow vane 100 rests on its overflow vane seat 104, and the working fluid 13 cannot circulate between the variable overflow pump volume 86 and the liquid cylinder 8.

[0345] When the hydraulic piston 10 of the compressor 3 reaches the high neutral position, the pressure P2 in the liquid cylinder 8 becomes substantially equal to the pressure P1 in the overflow reservoir 83, and the pressure applied to the valve actuation axial surface 99 is equal to the pressure applied to the liquid cylinder side axial surface 102.

[0346] From this situation, it is concluded that the actuating piston return spring 103 pushes the valve actuator piston 97 in the direction of the overflow vane 100 until the valve actuation axial surface 99 contacts the vane 100, and then the vane is lifted from its overflow vane seat 104, and this continues until the vane 100 reaches the maximum vane opening abutment portion 131.

[0347] The overflow vane 100 is removed from its overflow vane seat 104, the twin-body staged piston 89 can move under the action of its twin-body piston return spring 96, and discharge the working fluid 13 from the variable overflow pump volume 86 to the gas and liquid reservoir 14.

[0348] The hydraulic piston 10 of compressor 3 begins to descend again (this corresponds to...). Figure 5 When the pressure-volume diagram (cross section DE) is shown, the pressure P2 in the gas and liquid reservoir 14 and the liquid cylinder 8 becomes less than the pressure P1 in the overflow reservoir 83.

[0349] As a result, the valve actuator piston 97 compresses the actuator piston return spring 103. The valve actuator piston moves under the action of the pressure difference (i.e., P1 minus P2) between the pressure applied on its valve actuator axial surface 99 and the pressure applied on its liquid cylinder side axial surface 102. The piston 97 moves away from the overflow vane return spring 128, thereby causing the overflow vane 100 to return to contact its overflow vane seat 104.

[0350] exist Figure 20 and Figure 21 It should be noted that the overflow pump 82 of the expander 4 follows the same principle as the one just described. The difference is that the transfer of working fluid 13 from the overflow reservoir 83 to the liquid cylinder 8 does not occur when the hydraulic piston 10 reaches its high neutral position, but when the piston 10 reaches its low neutral position.

[0351] This is due to the fact that the average cycle of compressor 3 occurs at a pressure lower than the pressure in the pressure relief chamber 62 of compressor 3, while the average cycle of expander 4 occurs at a pressure higher than the pressure in the pressure relief chamber 62 of expander 4.

[0352] Therefore, in order to fill the variable overflow pump volume 86, the operation of the overflow pump 82 of the compressor 3 with respect to the pressure difference must preferably be the opposite of the operation of the overflow pump 82 of the expander 4.

[0353] As from Figure 9 It can be easily deduced that the control of the heat pump 55 is mainly performed by adjusting the rotational speed of the crankshaft 24 and adapting it to the motion pattern of the controlled expander valve 54, which is actuated to open and / or close by a valve actuator 119. The control of the speed and the actuator 119 is ensured by the computer 120.

[0354] In fact, all other things being equal, the power of the heat pump 55 is proportional to the rotational speed of its crankshaft 24, which is the first adjustment that allows the computer 120 to adjust the power.

[0355] However, apart from the rotational speed of its crankshaft 24, the more or less delayed and more or less staggered rise of the controlled expander valve 54 makes it possible, in particular, to adjust the pressure in the low-pressure gas reservoir 60 relative to the pressure in the high-pressure gas reservoir 58.

[0356] This adjustment is of great importance because the pressure difference discussed specifically determines the heat generated by the heat pump 55 during each rotation of the crankshaft 24.

[0357] For example, by making expander 4 in Figure 5 During the cross section FG of the diagram of the expander 4, less working gas 5 is transferred from the high-pressure gas reservoir 58 to the gas and liquid reservoir 14 than the working gas transferred by the compressor 3 during the cross section CD of the diagram. This has the effect of increasing the pressure in the high-pressure gas reservoir 58 and decreasing the pressure in the low-pressure gas reservoir 60.

[0358] Conversely, if expander 4 is in Figure 5During the cross section FG of the diagram, more working gas 5 is transferred from the high-pressure gas reservoir 58 to the gas and liquid reservoir 14 than the compressor 3 transfers during the cross section CD of the diagram. As a result, the pressure in the high-pressure gas reservoir 58 decreases, while the pressure in the low-pressure gas reservoir 60 increases.

[0359] It should be noted that, advantageously, the controlled expander valve 54 can behave as both a valve and a vane, that is, in addition to being opened by the valve actuator 119 of the controlled expander valve, it can also be opened by pressure differential.

[0360] In this respect, the valve 54 is preferably an autoclave, that is, during most of the thermodynamic cycle of the expander 4, the pressure difference between the inlet chamber 21 of the expander 4 and its gas and liquid reservoir 14 or the pressure difference between the depressurization chamber 62 of the expander 4 and the reservoir 14 tends to keep the valve 54 in close contact with the valve seat, which can be, for example, made of an elastomer or polymer O-ring housed in a recess.

[0361] However, if the pressure in the gas and liquid reservoir 14 of the expander 4 becomes greater than the pressure in the intake chamber 21 of the expander 4, the controlled expander valve 54 can open without the intervention of its valve actuator 119.

[0362] The same applies to the controlled expander valve 54, which is connected to the pressure relief chamber 62 of the expander 4 via the outlet port 7. If the pressure in the pressure relief chamber 62 becomes greater than the pressure in the gas and liquid reservoir 14 of the expander 4, the valve 54 can open without the intervention of its valve actuator 119.

[0363] from Figure 9 It can be easily deduced that when the heating and cooling device 106 placed under the floor inside the building 121 forms a heating element 18 connected to the heat export or input element 17 of the compressor 3, the heat pump 55 can operate in a "heating" mode, while the air-water exchanger 107 placed on the exterior 122 of the building 121 forms a cooling element 19 connected to the heat export or input element 17 of the expander 4.

[0364] If the heat pump 55 operates in "air conditioning" mode, the underfloor heating and cooling device 106 placed inside the building 121 forms a cooling component 19 connected to the heat export or input component 17 of the expander 4, while the air-water exchanger 107 placed outside the building 121 122 forms a cooling component 19 connected to the heat export or input component 17 of the compressor 3.

[0365] The change of mode can be easily performed by using one or more manual or electric valves (regardless of their type) to invert the heat transfer conduit 38, which was originally connected to the compressor 3, to become connected to the expander 4, and vice versa.

[0366] Please note that, except Figures 1 to 4 as well as Figures 6 to 23 In addition to the various components and accessories indicated, the mechanical liquid piston slow expansion compressor 1 and the resulting heat pump 55 according to the invention may also include a variety of other appliances and accessories, such as pressure and / or temperature sensors, frequency converters for adjusting the power supply to the electric drive motor 27, at least one angle decoder and / or pass-through sensors returning to the computer 120, speed and / or angular position of the crankshaft 24, one or more pumps and / or compressors and / or valves, purging devices, personnel safety elements, pressure limiters or discharge valves, or any other equipment known to those skilled in the art, enabling the transfer of working gas 5 or working liquid 13 from an external source to the high-pressure gas reservoir 58 or the low-pressure gas reservoir 60 or between said reservoirs 58, 60.

[0367] The heat pump 55 formed by the mechanical liquid piston slow expansion compressor 1 according to the invention may also include a thermal insulation layer 59 on all necessary components, and regardless of the nature of the layer 59, the layer may take the form of flexible or rigid thermal insulation foam or wool, brick, board or shielding that reflects radiation of any nature.

[0368] The thermal insulation layer 59 can insulate the heat pump 55 and its components from the environment outside the pump 55 and / or insulate the hot compressor 3 from the colder expander 4.

[0369] The heat pump 55 can also accommodate a soundproof enclosure, and its static frame 40 can be placed on the floor by means of vibration-resistant elastic studs.

[0370] The options of the mechanical liquid piston slow expansion compressor 1 according to the invention are not limited to the applications just described, and it must also be understood that the above description is given by way of example only and does not limit the scope of the invention in any way. Replacing the described implementation details with any other equivalent does not depart from the scope of the invention.

Claims

1. A mechanical liquid reciprocating slow-expansion compressor (1), the mechanical liquid reciprocating slow-expansion compressor defining a variable pneumatic volume (2), the variable pneumatic volume forming a compressor (3) or expander (4), wherein a working gas (5) is capable of entering the volume (2) via an inlet port (6) or exiting the volume (2) via an outlet port (7), the mechanical liquid reciprocating slow-expansion compressor being characterized in that it comprises: • Liquid cylinder (8), which is pivotable directly or indirectly about an inclined axis (9) perpendicular to the axis of the cylinder (8), and the liquid cylinder is fixed to a static frame (40). • A hydraulic piston (10) capable of being translated in a sealed manner within a liquid cylinder (8) to form a variable hydraulic volume (12) with the liquid cylinder, the variable hydraulic volume being wholly or partially filled with working fluid (13). • A gas and liquid reservoir (14) is connected to the variable hydraulic volume (12) via a connecting conduit (15) such that the reservoir (14) is mainly or entirely filled with working liquid (13) when the variable hydraulic volume (12) is at its minimum, and is wholly or partially filled with working gas (5) when the variable hydraulic volume (12) is at its maximum, wherein the change in the absolute volume of the working gas (5) contained in the variable pneumatic volume (2) forms the variable pneumatic volume (2) on the one hand, and on the other hand is approximately equal to the change in the absolute volume of the working liquid (13) contained in the variable hydraulic volume (12); • Heat exchange and accumulation component (16), which is housed in the gas and liquid reservoir (14), the component (16) being able to exchange heat with the working gas (5) or the working liquid (13) on the one hand, and temporarily store all or part of the heat on the other hand; • A heat export or import component (17) that directly or indirectly absorbs heat or directly or indirectly transfers heat to the heat exchange and accumulation component (16), and / or to the working liquid (13), and / or to the working gas (5), the absorbed heat being then transferred to a heating component (18), or the transferred heat being previously absorbed to a cooling component (19), the heating component (18) and the cooling component (19) being outside the gas and liquid reservoir (14); • Filling member (20), which allows or prevents the working gas (5) from being transmitted from the intake chamber (21) to the gas and liquid reservoir (14) via the inlet port (6); • Discharge member (22), which allows or prevents the working gas (5) from being transmitted from the gas and liquid reservoir (14) to the pressure relief chamber (62) via the outlet port (7); • Connecting rod (11), the first end (29) of which is securely fixed to the hydraulic piston (10), the rod (11) being approximately parallel to the longitudinal axis of the piston (10); • Piston guide member (23), which maintains the hydraulic piston (10) and the connecting rod (11) parallel to the cylinder (8), regardless of the position of the piston (10) in the cylinder (8); • Crankshaft (24), which is rotatable about an axis parallel to the inclined shaft (9) in at least one shaft bearing (25), and the crankshaft has at least one crank (26), the second rod end (30) of the connecting rod (11) being articulated about the at least one crank; • At least one drive motor (27) that directly or indirectly rotates the crankshaft (24). • Kinetic energy storage component (28), which is directly or indirectly connected to the crankshaft (24).

2. The mechanical liquid piston type slow expansion compressor according to claim 1, characterized in that, The inclined shaft (9) is a tubular ball joint (111) that terminates the liquid cylinder (8) and forms the connecting conduit (15) wholly or partially inside the tubular ball joint. The ball joint (111) is capable of being sealed and pivoted in a concave ball joint housing (123) fixed to the gas and liquid reservoir (14).

3. The mechanical liquid piston type slow expansion compressor according to claim 2, characterized in that, The tubular ball joint (111) receives at its center a ball joint shaft (124) parallel to the inclined axis (9), the shaft (124) being articulated about a ball joint tube bundle (125) directly or indirectly fixed to the gas and liquid reservoir (14).

4. The mechanical-liquid piston-type slow-expansion compressor according to claim 3, characterized in that, The spherical connector tube bundle (125) is connected to the gas and liquid reservoir (14) via an articulated tube bundle connector (126), and the tube bundle (125) is rotatable around the articulated tube bundle connector.

5. The mechanical liquid piston type slow expansion compressor according to claim 1, characterized in that, The liquid cylinder (8) and the gas and liquid reservoir (14) form a rigid assembly (31) which pivots about the tilting axis (9).

6. The mechanical liquid piston type slow expansion compressor according to claim 1, characterized in that, The heat exchange and accumulation component (16) is composed of a porous medium (32) with pores (33), and the working liquid (13) and the working gas (5) alternately enter and exit the porous medium.

7. The mechanical liquid piston type slow expansion compressor according to claim 1, characterized in that, The heat export or import component (17) consists of a circulation portion of the working fluid (13) which exits from the liquid cylinder (8) or from the gas and liquid reservoir (14) via a liquid outlet conduit (34) and returns to the cylinder (8) or the reservoir (14) via a liquid inlet conduit (35), after heat has been transferred to the heating component (18) or after heat has been drawn to the cooling component (19).

8. The mechanical liquid piston type slow expansion compressor according to claim 1, characterized in that, The heat export or import component (17) is comprised of at least one heat exchanger conduit (36) housed in the gas and liquid reservoir (14), and a heat transfer fluid (37) circulates in the at least one heat exchanger conduit, which transfers the heat drawn or transferred to the heat exchange and accumulation component (16), and / or to the working liquid (13), and / or to the working gas (5) via the heat transfer conduit (38) all the way to the cooling component (19) or the heating component (18).

9. The mechanical liquid piston type slow expansion compressor according to claim 1, characterized in that, The heat exchange and accumulation component (16) consists of at least one liquid spray nozzle (71), which is supplied by a liquid spray pump (72). The nozzle (71) is capable of atomizing the working liquid (13) into fine droplets in the internal volume of the gas and liquid reservoir (14).

10. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The tilting shaft (9) is composed of a rolling track (41), which is fixed to the static frame (40) and directly or indirectly fixed to the rolling surface (42) of the liquid cylinder (8) and is capable of rolling on the rolling track; The contact line between the base circle (44) of the rolling track gear (43) and the rolling track (41) and the rolling surface (42) which is directly or indirectly fixed to the liquid cylinder (8), fixed to the static frame (40), and engaged with the rolling surface gear (45) coincides.

11. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The piston guide member (23) is composed of a sliding pivot connection (47), which is formed between the outer cylindrical surface (48) of the connecting rod (11) and the sliding ring (49) which is fixedly connected to the liquid cylinder (8) by means of an annular carrier structure (50).

12. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The piston guide member (23) is composed of a guide skirt (57) disposed around the periphery of the hydraulic piston (10), and the skirt (57) is capable of translating in the cylinder (8) with a low clearance.

13. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The filling member (20) and / or the discharge member (22) are composed of at least one compressor vane (52) and / or at least one controlled compressor valve (53). However, in operation, the working gas (5) is discharged from the reservoir (14) via the pressure relief chamber (62) at a pressure greater than the pressure at which it was previously introduced into the gas and liquid reservoir (14) via the intake chamber (21), while the heat export or import member (17) transfers heat to the heating member (18), such that the variable pneumatic volume (2) forms the compressor (3).

14. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The filling member (20) and / or the discharge member (22) are constituted by at least one controlled expander valve (54). However, in operation, the working gas (5) is discharged from the reservoir (14) via the pressure relief chamber (62) at a pressure lower than that at which it was previously introduced into the gas and liquid reservoir (14) via the inlet chamber (21), while the heat export or import member (17) draws heat to the cooling member (19), so that the variable pneumatic volume (2) forms an expander (4).

15. The mechanical-liquid piston-type slow-expansion compressor according to claims 13 and 14, characterized in that, The pressure relief chamber (62) of the compressor (3) is connected to the intake chamber (21) of the expander (4) via a high-pressure gas conduit (56), such that the working gas (5) depressurized via the pressure relief chamber (62) of the compressor (3) is introduced into the expander (4) via the intake chamber (21) of the expander (4), the crankshaft (24) of the compressor (3) is directly or indirectly connected to the crankshaft (24) of the expander (4), and the compressor (3) and the expander (4) are coupled to form a heat pump (55).

16. The mechanical-liquid piston-type slow-expansion compressor according to claim 15, characterized in that, The high-pressure gas conduit (56) is connected to at least one high-pressure gas reservoir (58).

17. The mechanical-liquid piston type slow-expansion compressor according to claim 15, characterized in that, The intake chamber (21) of the compressor (3) and the pressure relief chamber (62) of the expander (4) are connected by a low-pressure gas reservoir (60), and the intake chamber and the pressure relief chamber are respectively connected to the low-pressure gas reservoir through a low-pressure gas conduit (61).

18. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The air intake chamber (21) and the pressure relief chamber (62) are located in the upper part of the gas and liquid reservoir (14), which is itself located above the liquid cylinder (8), such that due to gravity, the working gas (5) always leaves the gas and liquid reservoir (14) first via the pressure relief chamber (62), and the working liquid (13) always enters the reservoir (14) first via the air intake chamber.

19. The mechanical liquid piston type slow expansion compressor according to claim 5, characterized in that, The inclined shaft (9) is formed by a hollow cylindrical shaft (63) having at least one open radial space (64) positioned above the gas and liquid reservoir (14), and the inlet chamber (21) and / or the pressure relief chamber (62) are connected to an annular gas collector (65) surrounding the cylindrical shaft (63) and including the open radial space (64) so ​​that the working gas (5) can circulate between the hollow cylindrical shaft (63) and the inlet chamber (21) and / or the pressure relief chamber (62) via the open radial space (64) and the annular gas collector (65).

20. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The kinetic energy storage component (28) is composed of a low-speed inertial flywheel (66), which is rotatably fixed to the crankshaft (24) on one hand and rotatably fixed to the ring gear (67) on the other hand. The drive motor (27) rotates the ring gear by means of at least one ring drive pinion (68), the base circle diameter of which is smaller than the base circle diameter of the ring (67). The ring and the pinion (68) form a high transmission ratio meshing system (69). However, the high-speed inertial flywheel (70) is rotatably fixed to the ring drive pinion (68) directly or indirectly.

21. The mechanical-liquid piston type slow-expansion compressor according to claim 9, characterized in that, The liquid spray pump (72) comprises: a pump cylinder (73) disposed in the liquid cylinder (8) and / or in an extension of the cylinder (8); and a pump piston (74) movable by the hydraulic piston (10) and / or by the liquid cylinder (8), the pump piston being capable of translation within the pump cylinder (73).

22. The mechanical-liquid piston type slow-expansion compressor according to claim 21, characterized in that, The pump piston (74) includes a stroke start contact pin (77), the pump piston moves by means of the stroke start contact pin, and the piston (74) returns to the stroke end contact part (78) by the piston return mass (76).

23. The mechanical liquid piston type slow expansion compressor according to claim 21, characterized in that, The pump piston (74) moves by means of a moving spring (81).

24. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, During each rotation of the crankshaft (24), the overflow pump (82) transfers a small amount of working fluid (13) from the overflow reservoir (83) to the gas and liquid reservoir (14) and / or the liquid cylinder (8).

25. The mechanical-liquid piston type slow-expansion compressor according to claim 24, characterized in that, The overflow reservoir (83) is connected to the pressure relief chamber (62), and the working gas pressure (5) in the reservoir (83) is close to or equal to the working gas pressure in the pressure relief chamber (62).

26. The mechanical-liquid piston type slow-expansion compressor according to claim 24, characterized in that, The overflow pump (82) includes a pump blind cylinder (84), an overflow pump piston (85) capable of being hermetically translated within the pump blind cylinder, the overflow pump piston and the cylinder (84) forming a variable overflow pump volume (86), the variable overflow pump volume being filled with working fluid (13) from the overflow reservoir (83) via at least one overflow pump inlet vane (87) when it increases, and the variable overflow pump volume depressurizing the fluid (13) to the gas and liquid reservoir (14) and / or the liquid cylinder (8) via a pressure relief valve (88) when it decreases.

27. The mechanical-liquid piston type slow-expansion compressor according to claim 26, characterized in that, The overflow pump piston (85) is a double-body staged piston (89), which includes a large-diameter body (93) having a large cross-sectional surface (90) forming one of the walls of the variable overflow pump volume (86). The staged piston (89) also includes a small-diameter body (94) axially opposite to the large cross-sectional surface (90), which is capable of being hermetically translated within an actuating cylinder (92) whose internal volume is directly or not directly connected to the internal volume of the liquid cylinder (8). The small-diameter body (94) includes a surface (91) with a small cross-section, and pressure in the liquid cylinder (8) is applied to the surface with the small cross-section. On the cross-sectional surface, the graded piston (89) also provides a surface (95) with an average cross-section at the junction between the large-diameter body (93) and the small-diameter body (94), the small-diameter body (94) protruding from the surface with an average cross-section, the surface with an average cross-section connected to the overflow reservoir (83), and the surface with an average cross-section subjected to pressure in the reservoir (83), while the graded piston abutment (117) fixes the maximum volume of the variable overflow pump volume (86), and the double-body piston return spring (96) tends to push against the double-body graded piston in the direction of the surface (90) with a large cross-section of the double-body graded piston (89).

28. The mechanical-liquid piston type slow-expansion compressor according to claim 27, characterized in that, The pressure relief valve (88) includes a valve actuator piston (97) capable of being hermetically translated within a valve actuator cylinder (98), and the valve actuator piston firstly having a valve actuation axial face (99) communicating with the overflow reservoir (83), and the pressure in the reservoir (83) being applied to the valve actuation axial face. When the valve actuator piston (97) moves in the direction of the face (99), the face (99) enables the overflow vane (100) to rise from the overflow vane seat (104), which has the effect of communicating the variable overflow pump volume (86) via the overflow vane (100) with the gas and liquid reservoir (14) and / or the liquid cylinder (8); and the valve actuator piston secondly having a liquid cylinder side shaft. The liquid cylinder side axial surface (102) is connected to the liquid cylinder (8). The pressure in the cylinder (8) is applied to the liquid cylinder side axial surface. When the valve actuator piston (97) moves in the direction of the liquid cylinder side axial surface (102), the liquid cylinder side axial surface can contact the liquid cylinder side abutment (118). However, the actuator piston return spring (103) tends to push the valve actuator piston in the direction of the valve actuator piston (97) valve actuator axial surface (99), and the overflow vane return spring (128) tends to cause the overflow vane (100) to return to contact the overflow vane seat (104) it engages with. The force generated by the actuator piston return spring (103) is greater than the force generated by the overflow vane return spring (128).

29. The mechanical-liquid piston-type slow-expansion compressor according to claim 26, characterized in that, The overflow pump piston (85) is a double-body staged piston (89), which includes a large-diameter body (93) having a large cross-sectional surface (90) connected to and subjected to pressure in the overflow reservoir (83). The staged piston (89) also includes a small-diameter body (94) axially opposite to the large cross-sectional surface (90), which is capable of being translated hermetically within an actuating cylinder (92) whose internal volume is directly or indirectly connected to the internal volume of the liquid cylinder (8). The small-diameter body (94) includes a surface (91) with a small cross-section in the liquid cylinder. The pressure in (8) is applied to the surface with a small cross-section, and the graded piston (89) also provides a surface (95) with an average cross-section at the junction between the large-diameter body (93) and the small-diameter body (94), the small-diameter body (94) protruding from the surface with an average cross-section, the surface (95) forming one of the walls of the variable overflow pump volume (86), while the graded piston abutment (117) fixes the maximum volume of the variable overflow pump volume (86), and the double-body piston return spring (96) tends to push against the double-body graded piston in the direction of the surface (91) with a small cross-section of the double-body graded piston (89).

30. The mechanical liquid piston type slow expansion compressor according to claim 29, characterized in that, The pressure relief valve (88) includes a valve actuator piston (97) capable of being hermetically translated within a valve actuator cylinder (98). The valve actuator piston first has a valve actuation axial face (99) communicating with the liquid cylinder (8), and pressure in the cylinder (8) is applied to this axial face. When the valve actuator piston (97) moves in the direction of this face (99), the face (99) allows an overflow vane (100) to rise from an overflow vane seat (104). This has the effect of communicating the variable overflow pump volume (86) via the overflow vane (100) with the gas and liquid reservoir (14) and / or the liquid cylinder (8). The valve actuator piston also has a reservoir-side axial face (101). The reservoir side axial surface is connected to the overflow reservoir (83). The pressure in the reservoir (83) is applied to the reservoir side axial surface. When the valve actuator piston (97) moves in the direction of the reservoir side axial surface (101), the reservoir side axial surface can contact the overflow reservoir side abutment (130). However, the actuator piston return spring (103) tends to push the valve actuator piston in the direction of the valve actuator piston (97) valve actuator axial surface (99), and the overflow vane return spring (128) tends to return the overflow vane (100) to contact the overflow vane seat (104) it engages with. The force generated by the actuator piston return spring (103) is greater than the force generated by the overflow vane return spring (128).

31. The mechanical-liquid piston-type slow-expansion compressor according to claim 1, characterized in that, The balancing member (112) completely or partially replaces the piston guide member (23) to tilt the liquid cylinder (8) during rotation of the crankshaft (24).

32. The mechanical-liquid piston-type slow-expansion compressor according to claim 31, characterized in that, The balancing component (112) is composed of a balancing mast (113), which includes a balancing mass (116) on one hand and a mast axis (114) that is parallel to the tilt axis (9) of the liquid cylinder (8) and fixed to the static frame (40) on the other hand. However, the balancing mast (113) forms a pivot-sliding joint movement part (115) with the cylinder (8) and constitutes an imbalance opposite to the imbalance of the cylinder (8).

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