• 专利附录
  • 专利说明
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    • 专利摘要:
    The present invention relates to an external hot-spring engine comprising: - at least one cylinder (2), - a movable piston (3) reciprocating in the cylinder, - a cylinder head (4) defining a working chamber (5) with the piston and the cylinder, - a heat exchanger (6) between a working gas and a coolant, - a distribution comprising two rotary plugs (20, 30) rotatably mounted in the cylinder head and selectively communicating the chamber of work with the following resources:? an admission (A) of working gas,? a cold end (B) of the exchanger, a hot end (C) of the exchanger, an exhaust (D). The bushings (20, 30) comprise internal passages opening through their side wall by at least one mouth which selectively communicates with the working chamber (5) by at least one light made in the yoke (4).
    公开号:FR3069884A1
    申请号:FR1757398
    申请日:2017-08-02
    公开日:2019-02-08
    发明作者:Olivier Thevenod Frederic
    申请人:H2p Systems；
    IPC主号:
    专利说明:

    "External hot-plug engine"
    Technical area
    The present invention relates to an external hot source engine.
    State of the art
    Engines with an external hot source, for example of the Ericsson type, are experiencing renewed interest and development, with the aim of reducing pollutant emissions or reducing energy consumption by upgrading heat emissions. This type of engine operates between two heat sources external to the engine via exchangers. It uses valves to control the flow of the working fluid (in the gas phase) between two chambers, one for compression and the other for expansion.
    For volumetric machines such as in particular internal combustion piston engines, distributions are also known using valves actuated by cams. This type of distribution has various limitations. In particular, the pressure on the face of the valve opposite the working chamber must be low. In addition, the maximum valve lift is low if the duration (measured in degrees of cam rotation angle) of the valve opening is short. In addition, the cam drive consumes energy.
    Volumetric machines are also known, such as compressors, which use a valve distribution. This solution requires that the pressure differential on each valve always has, at each stage of the machine operating cycle, an appropriate value and direction so that the valve is in the state - open or closed necessary at the considered stage of the cycle .
    In certain volumetric machines with an external hot source, such as those described in the two patent applications FR. 2,905,728 and FR. 2,954,799, the working gas is compressed in a working chamber, then transferred to a hot source, and from there re-transferred to the same working chamber at the start of an expansion time of this chamber. To be effective, the two aforementioned transfers of working gas must be brief and take place through a passage section large enough to minimize the pressure drops. These requirements are difficult to meet with distribution by valves controlled by cams. Furthermore, this type of cycle is hardly compatible with distribution by valves.
    The object of the present invention is to propose an engine with an external hot source making it possible to at least partially remedy the problems mentioned above. It also aims to provide a space-saving motor.
    Statement of the invention
    According to a first aspect of the invention, at least one of the objectives is achieved with an external hot source engine comprising:
    - at least one cylinder,
    - a piston moving back and forth in the cylinder,
    - a cylinder head defining, with the piston and the cylinder, a working chamber for a working gas,
    - a distribution mounted in the cylinder head and selectively communicating the working chamber with the following resources:
    o a working gas inlet, o a cold end of a heat exchanger, o a hot end of the heat exchanger, o an exhaust.
    According to the invention, the distribution comprises at least one rotary plug mounted in rotation in the cylinder head and has internal passages opening out through its side wall by at least one mouth which communicates selectively with the working chamber by at least one light provided in the breech.
    The engine according to the invention has the advantage, compared with devices comprising valves, of distributing gas flows with little pressure drop, via large passage sections for very short instants. Compared to an engine implementing an ERICSSON cycle, the engine according to the invention makes it possible to significantly divide the friction and the pressure losses. It improves engine efficiency while reducing the number of parts and thus the size and weight of the engine.
    By bushel is meant a cylindrical element comprising internal passages in which the working gas can circulate. An internal passage is for example a conduit. The plug is arranged so that its axis of rotation is perpendicular to the axis of the cylinder above which it is arranged. The plug is located between the working chamber and the exchanger along the working gas path. The rotary movement of the plug is synchronized with the reciprocating movement of the piston, so that the working gas can pass through the plug via the internal passages, and thus distribute the gas between the working chamber and the exchanger. Preferably, each internal passage communicates with at least two openings made through the side wall of the plug, each opening being located at one of the two ends of the internal passage. At a certain stage of the cycle, the working gas flows between the working chamber and the cold inlet of the exchanger by passing through at least one lumen of the cylinder head and at least one internal passage of the rotating plug. The mouth is called an opening in the plug which selectively coincides with at least one lumen made in the cylinder head.
    The valve distribution system makes it possible to propose a large cross-section for the passage of the working gas, in particular as soon as a mouth begins to coincide with a lumen of the cylinder head. As the rotational speed of the plug is substantially constant, the passage section increases rapidly, for example linearly, until the mouth coincides perfectly with the lumen of the cylinder head. On the contrary, by its geometry (substantially ovoid), a cam actuates a valve according to a substantially sinusoidal law so that the cross section of the working gas increases very slowly at the start of the opening movement.
    The ball valve distribution makes it possible to perform the thermodynamic cycle, of the four-stroke type, as follows:
    - a working gas, appreciably cold, is admitted into the working chamber,
    - said gas is compressed in said working chamber, then
    - transferred to the exchanger in which a heat transfer fluid (the hot source) circulates, so as to heat the working gas;
    - The heated working gas is re-transferred to the working chamber at the start of an expansion time of the same working chamber; then
    - the expansion continues and ends while the working chamber is isolated from the exchanger; and
    - the working gas is escaped from the working chamber.
    Thanks to the bushel, the two aforementioned transfers of the working gas are brief and take place through a passage section large enough to minimize the pressure drops.
    Preferably, at least one lumen of the cylinder head is capable of communicating with two internal passages of the plug which open out through the lateral wall of the plug via two mouths aligned circumferentially. The angular difference between the two adjacent mouths is between 5 and 15 degrees. These values, like the angular values given below, for the mouthpieces and the orifices, are indicated for a rotation speed of the plug between 3000 and 4000 rpm (revolutions per minute) and a temperature of the heat transfer fluid between 500 ° C and 600 ° C (degrees Celsius). Said two internal passages are, one, a passage through which the working gas enters the working chamber, and the other, a passage through which the working gas leaves the working chamber. This characteristic allows a working gas leaving the working chamber, and a working gas entering the working chamber, to cross. This avoids an unfavorable phenomenon of relatively low pressure in the working chamber at the start of the expansion phase.
    For example, the bushel includes:
    an internal passage intended to circulate the cold and compressed working gas between the working chamber and the cold end of the exchanger, and
    - An internal passage, distinct from the previous one, intended to circulate the working gas, compressed and heated, between the hot end of the exchanger and the working chamber.
    The working gas entering the exchanger is said to be "cold" by comparison with its higher temperature when it leaves "hot" from the exchanger. It should however be understood that the "cold" working gas entering the exchanger is already heated by its compression in the working chamber. Likewise, the “cold” end of the exchanger is still at a temperature close to that of the working gas at the end of compression.
    Preferably, the distribution is arranged so that, towards the end of the compression, the working chamber begins to communicate with the cold end of the exchanger when the pressure in the working chamber is lower than the pressure in the exchanger. When the engine is running and with reference to the cycle described above, the cold and compressed and / or being compressed working gas enters the rotating plug as soon as at least part of the mouth coincides with the light so as to circulate the cold and compressed working gas towards the cold end of the exchanger. The passage section between the working chamber and the mouth increases with the rotation of the plug. When the mouth of the bushel coincides perfectly with the lumen of the cylinder head, the passage section is maximum. The major part, at least 50%, of the volume of cold and compressed working gas then passed through said mouth. Then, due to the rotation of the plug and the end of the compression, only part of the mouth coincides with the lumen, so as to circulate the remaining part of the cold and compressed working gas towards the cold end of the exchanger. Simultaneously, the passage section between the working chamber and the second mouth, of the second internal passage, increases so that part of said mouth coincides with the same lumen. The working gas leaving the second mouth, and therefore entering the working chamber, comes from the hot end of the exchanger after being heated. The working gas thus makes a loop passing through the same lumen of the cylinder head but through different internal passages of the plug. This makes it possible to produce said larger light, and therefore to further increase the passage section offered to the gas to pass into and out of the exchanger. For a short time the cold working gas and the hot working gas intersect.
    In one embodiment, at the end opposite to the mouths, the internal passages open out through the side wall of the plug through orifices which communicate selectively with fixed fittings according to the angular position of the plug. The plug holes allow the working gas to flow from the internal passages of the plug to the fittings or from fittings to the internal passages of the plug.
    Preferably, for each internal passage, the geometry of the at least one bushel is such that the orifice is capable of communicating with the corresponding fitting when the mouth communicates with the working chamber. This feature allows the working chamber to communicate with the fittings, so as to circulate the working gas.
    Said fittings include a cold fitting communicating with the cold end of the exchanger and a hot fitting communicating with the hot end of the exchanger. Said fittings include an intake fitting communicating with the inlet of the working gas and an exhaust fitting communicating with the exhaust of the working gas.
    For the above and for the rest of the application, the terms mouth and orifice correspond to or qualify openings made through the side wall of the plug. The term mouth is used to qualify each opening capable of communicating with the light from the cylinder head for the passage of the working gas from the working chamber to the plug or vice versa. The term orifice is used to describe each opening capable of communicating with a fitting for the passage of working gas from the bushel to the fitting or vice versa. A mouthpiece cannot be used as an orifice and vice versa. For this, on the side wall of the at least one plug, the at least one mouth is offset axially with respect to the at least one orifice.
    According to one embodiment, the mouths and orifices or openings of the plug are only arranged through the side wall.
    According to another embodiment, the mouths and orifices or openings of the plug can be arranged, in part or only, through the two axial faces of the plug.
    According to a preferred embodiment, the engine comprises a low pressure plug controlling the selective communication of the working chamber with the intake and the exhaust. The engine includes a high pressure plug controlling the selective communication of the working chamber with the hot and cold ends of the exchanger. This characteristic makes it possible to simplify the construction of the engine by dissociating the so-called “high pressure” flows from the so-called “low pressure” flows and reducing its size. The bushels can have identical or different diameters. Bushels of identical diameter simplify the construction of the engine. This embodiment also satisfies the concern of providing a relatively large passage section for the gas going to and from the exchanger, since the gas then being compressed, the volume which must flow is smaller than at the inlet and at the exhaust. However, a high pressure bushel with a diameter greater than the diameter of the low pressure bushel makes it possible to further enlarge the passage section of the internal passages, going to the exchanger and returning.
    Preferably, the engine comprises two fixed fittings, a so-called “high pressure” fitting and a so-called “low pressure” fitting. The high pressure connection comprises a cold connection communicating with the cold end of the exchanger and a hot connection communicating with the hot end of the exchanger. The low pressure fitting includes an inlet fitting and an exhaust fitting.
    According to a preferred embodiment, the thermodynamic cycle is carried out in a single cylinder. The cylinder head, surmounting the working chamber, supports the high pressure plug and the low pressure plug, which are arranged parallel to each other seen parallel to the axis of the plug. The cylinder head has a general geometric shape evoking a triangle. It has a lower face and two curvilinear side faces whose upper ends meet.
    The cylinder head has two concave and opposite lateral faces, each face being arranged to receive a cylindrical plug, by complementarity of shape. In particular, each lateral face has a section in the form of an arc of a circle substantially coaxial with the axis of the received bushel. The lights are made in the side faces. Preferably, the lights are rectangular in shape to limit the pressure drops.
    The cylinder head has a substantially planar underside intended to be in contact with the engine liner. The underside includes a chamber opening which defines the entrance to a transition cavity and which, during engine operation, extends the volume of the working chamber (similar in shape to the shape of the cylinder) seen parallel to the 'axis of bushels. The transition cavity has a substantially triangular shape. Preferably, the piston head has a shape complementary to the shape of the transition cavity, so that the head can enter the transition cavity.
    According to one embodiment, the at least one mouth includes two mouths for the same internal passage, capable of communicating simultaneously with the working chamber, by two lights. Each mouthpiece can coincide with a light. This characteristic is particularly advantageous with a view to finding a compromise between a large passage section for the flow of the working gas, limiting the pressure drop of said flow and limiting the leaks of working gas between the plug and the cylinder head. This compromise is all the more important for the high pressure bushel.
    For example during the compression phase of the working gas and during its routing towards the cold end of the exchanger, the gas passes into the two mouths of the high pressure bushel by crossing the two lumens of the cylinder head so that the flow is divided in two to cross the two lights and the two mouths, forming two flow lines. After the two mouths, each flow line flows in a conduit opening into a common conduit. The internal passage in fact has the shape of a Y according to this particular embodiment.
    Preferably, the lights and the mouths have a rectangular shape to limit the pressure drops.
    Preferably, at least one of the mouths is subdivided by at least one mullion. This characteristic makes it possible to support sealing devices, placed on the cylinder head, when the at least one mouth passes in front of a lumen of the cylinder head. The mullions can equip both the mouths of the low pressure bushel and those of the high pressure bushel.
    For the above and for the following description, the term mullion means a bar intended to subdivide only the mouth without protruding inside the plug (without dividing the internal passage). It extends circumferentially to connect two longitudinal sides of a mouthpiece so as to extend the circumference of the plug.
    According to another embodiment, which may be compatible with the previous embodiment, at least one passage comprises two passages leading in parallel to the same resource, capable of simultaneously communicating each with a respective light from the cylinder head. This characteristic makes it possible to propose a large passage section for the working gas.
    For example during the return of the working gas coming from the hot end of the exchanger, the flow of the working gas is divided into two flow lines, which circulate in two separate internal passages inside the plug. The two flow lines are divided before the entry in the two orifices of the plug and join after the exit of the two lights of the cylinder head.
    Preferably, the shape of the sections and the layout of the internal passages are made to promote the circulation of the working gas in precise directions, for example to promote the suction of the gas, in particular to avoid a compression effect in the plug. In addition they are arranged to limit the differential pressures along each bushel. This makes it possible to limit the friction between the plug and the cylinder head and thus limit the risks of leakage of working gas around the plug.
    According to other embodiments, the external hot source engine can comprise several cylinders such as an internal combustion engine. For example, the engine may include at least two cylinders. In this case, it can include all or part of the characteristics described so far. The at least one bushel may comprise two orifices aligned circumferentially to communicate selectively with the same fitting, and which each communicate with a respective passage associated with a respective one of the cylinders. This characteristic makes it possible to reduce the size of the plug and therefore the size of the motor.
    The orifices are opposite, for example 180 degrees, and the internal passages upstream of said orifices are adjoining and have a common wall.
    In the case of two or more cylinders, the plug is advantageously the same for all the cylinders which are arranged in line with one another.
    Preferably, the engine includes sealing devices to limit gas leaks. The lights are surrounded by sealing devices to close the gap between the peripheral wall of the plug and an adjacent surface of the cylinder head all around each light. The sealing device may comprise bars of a material for dry friction, for example graphite. For example, the bars are arranged on the lateral faces of the cylinder head around the lights.
    According to another aspect of the invention, which may be compatible with the first aspect, there is provided a motorization assembly comprising a motor according to one or more of the characteristics set out above and a heat exchanger having a heat transfer path s' extending between a cold end and a hot end selectively connected to the working chamber towards the end of a compression phase and towards the start of an expansion phase, respectively. The working gas circulates in the heat-receiving path.
    Preferably, the exchanger is of the counter-current type. The heat exchanger comprises a heat transfer path traversed in one direction by a heat transfer fluid, which direction is opposite to the direction of travel of the working gas in the heat transfer path. The heat transfer path is distinct from the heat transfer path.
    According to one embodiment, the heat exchanger comprises a heat transfer path traversed by the exhaust gases of an internal combustion engine. According to another embodiment, the heat exchanger comprises a heat transfer path traversed by a fluid heated with solar energy.
    Description of the figures and embodiments
    Other advantages and particularities of the invention will appear on reading the detailed description of implementations and embodiments in no way limiting, and the following appended drawings:
    - Figures la, lb, 2a, 2b and 2c are schematic representations of an external hot source engine, comprising two rotary plugs according to the invention, the engine being coupled with a heat exchanger, the engine and exchanger assembly being seen in section during the main operating phases of the engine: FIG. 1a illustrating a phase of admission of a working gas into the cylinder of the engine, FIG. 1b illustrating a phase of exhaust of gas from said cylinder, FIG. 2a illustrating a phase of end of compression of the working gas and during which the gas is also directed towards a cold end of the heat exchanger, FIG. 2b illustrating a phase in which a bushel has a position known as “of scanning ”which authorizes the simultaneous fluid communication of the cold end and the hot end of the exchanger with the engine cylinder, FIG. 2c illustrating a phase of expansion of the working gas after passing through the exchanger;
    - Figure 3 is a bottom view in perspective of a cylinder head, according to one embodiment, provided for an engine comprising two cylinders, the cylinder head having four slots for each cylinder;
    - Figure 4 is an exploded perspective view of an upper part of an engine, according to an embodiment comprising two cylinders, the upper part comprising a cylinder head, according to Figure 3, carrying on the one hand a bushel said "Low pressure" covered with a fitting, and on the other hand a plug called "high pressure" which is seen exploded between the cylinder head and a fitting provided to cover the high pressure plug;
    - Figures 5a, 5b, 6a and 6b are views showing the angular position of the plugs before and after the phase illustrated in Figure 2b, Figures 5a and 6a illustrating in particular the high pressure plug, according to a mode of representation similar to that of FIG. 4, FIGS. 5b and 6b being sectional views of an entire motor, FIGS. 5a and 5b illustrating the angular position of the high pressure plug just before the scanning position and FIGS. 6a and 6b illustrating the position angle of the high pressure plug just after the sweep position;
    FIGS. 7a and 7b are views showing the angular position of the plugs during the intake phase of the working gas illustrated by FIG. 1a, FIG. 7a is a perspective view of an upper part of an engine, according to an embodiment comprising two cylinders, the upper part comprising a cylinder head carrying on the one hand a high pressure bushel covered with a fitting, and on the other hand a low pressure bushel which is seen exploded between the cylinder head and a fitting provided to cover the low pressure plug, FIG. 7a illustrating in particular the orientation of the low pressure plug along its axis of rotation, FIG. 7b being a sectional view of an entire engine;
    - Figures 8a and 8b are views showing the angular position of the plugs during the exhaust phase of the working gas illustrated in Figure lb, Figure 8a is a perspective view according to Figure 7a and illustrating the orientation of the low pressure plug along its axis of rotation, FIG. 8b being a sectional view of an entire engine.
    As these embodiments are in no way limitative, it will in particular be possible to consider variants of the invention comprising only a selection of characteristics described below isolated from the other characteristics described (even if this selection is isolated within a sentence including these other features), if this selection of features is sufficient to confer a technical advantage or to differentiate the invention from the state of the prior art. This selection comprises at least one characteristic, preferably functional, without structural details, and / or with only part of the structural details if this part only is sufficient to confer a technical advantage or to differentiate the invention from the state of the art. earlier.
    FIGS. 1a, 1b, 2a, 2b and 2c illustrate the main phases of operation of an external hot source engine 1, and will make it possible to describe the engine, according to an embodiment comprising the essential characteristics. The engine includes:
    - an engine block in which is formed a cylindrical cavity called cylinder 2,
    a mobile piston 3 arranged to move back and forth in the cylinder 2,
    a cylinder head 4 covering the engine block above the cylinder 2, a working chamber 5 being delimited for a working gas, typically air, in the cylinder 2 between the piston 3 and the cylinder head 4,
    a distribution mounted in the cylinder head 4, arranged and configured to selectively communicate the working chamber 5 with the following resources:
    o an inlet A for working gas, o a cold end B of a heat exchanger, o a hot end C of the heat exchanger, o an exhaust D.
    The engine is connected to a heat exchanger 6 for a heat exchange between the working gas, called heat transfer fluid, and a heat transfer fluid. The heat exchanger 6 is of the counter-current type. It includes a heat transfer path 61 traveled by the heat transfer fluid from left to right. It further comprises a heat-receiving path 62, shown under the heat-yielding path 61, with reference to FIGS. 1a to 2c, so that the working gas traverses the heat-receiving path from right to left. The heat transfer path is distinct from the heat transfer path. The heat transfer fluid is for example the exhaust gases of an internal combustion engine.
    The heat exchanger 6 is connected to the engine by means of fittings and pipes so as to be able to circulate the working gas from the engine to the exchanger and vice versa. Similarly, one or more fittings or pipes are connected to the engine to produce the intake and exhaust.
    The distribution comprises two rotary plugs 20, 30 mounted in rotation in the cylinder head 4, above the working chamber 5. The axes of rotation of the two plugs are parallel to each other and orthogonal to the axis of the cylinder 2. The plugs comprise a plug called “low pressure” 30 arranged and configured to control the selective communication of the working chamber 5 with the inlet A and the exhaust D. The plugs include a plug called “high pressure” 20 arranged and configured to control the selective communication of the working chamber 5 with the hot C and cold B ends of the exchanger 6. Preferably, the high pressure valve 20 is used only to control the circulation of the working gas between the chamber of work and the exchanger. Likewise, the low pressure bushel is used only to control the intake and exhaust. This characteristic makes it possible to simplify the construction of the engine by dissociating the so-called “high pressure” flows from the so-called “low pressure” flows and reducing its size. The bushels have identical diameters to simplify the construction of the engine.
    Each plug 20, 30 includes internal passages for conducting the working gas between the working chamber 5 and the resources. Each internal passage has two ends which open out through the side wall of a plug each through at least one opening. The distribution is arranged and configured so that the rotary movements of the plugs are synchronized with the reciprocating movement of the piston, so that the working gas can pass through the plugs via the internal passages. The openings are arranged and configured to selectively coincide with at least one lumen formed in the cylinder head and at least one lumen formed in a fixed connector. The opening opposite the lumen of the cylinder head when the working gas passes between the working chamber and the plug or vice versa is called the mouth. The orifice is called the opening opposite a fitting during the passage of the working gas between the plug and said fitting or vice versa. A mouthpiece cannot be used as an orifice and vice versa. For this, the orifices have an axial offset with the mouths.
    According to one embodiment of an engine comprising a single cylinder, the low pressure plug comprises:
    - for inlet A, an internal passage comprising an inlet mouth and an inlet orifice,
    - for the exhaust D, an internal passage comprising an exhaust mouth and an exhaust orifice, and the high pressure plug comprises:
    for the transfer of the working gas from the working chamber 5 to the cold end B of the exchanger 6, an internal passage comprising at least one cold mouth and at least one cold orifice,
    - For the transfer of the working gas from the hot end C of the exchanger 6 to the working chamber 5, an internal passage comprising at least one hot mouth and at least one hot orifice.
    The ball valve distribution makes it possible to carry out the thermodynamic cycle whose main phases will now be described.
    With reference to FIG. 1a, the phase of admission of a working gas into the working chamber 5 is illustrated. The synchronization of the piston 3 and of the plugs 20, 30 is such that the movement of the piston 3 is descending during that the rotation of the low pressure bushel 30 allows an inlet mouth 32 of the low pressure bushel to communicate with a light from the cylinder head and simultaneously allows an inlet port 34 to communicate with a light from an intake fitting . The working gas passes through the internal passage between the inlet orifice and the inlet mouth so as to be admitted into the working chamber 5. At the same time, no mouth of the high pressure plug communicates with a light from the cylinder head. . The working gas is preferably air taken from the outside environment. When the piston has reached bottom dead center, the low pressure valve 30 has pivoted so that the inlet mouth 32 of the low pressure valve no longer communicates, even partially, with a light from the cylinder head (excluding any closing delay admission).
    Then the piston rises so that the trapped working gas is compressed in the working chamber. Referring to Figure 2a, there is illustrated a phase of end compression of the working gas. The synchronization of the piston 3 and of the bushels 20, 30 is such that the movement of the piston 3 is ascending while the rotation of the high pressure bushel 20 allows a cold mouth 21 of the high pressure bushel to communicate with a light from the cylinder head and simultaneously allows a cold orifice 23 to communicate with a lumen of a connector of the cold end B of the exchanger 6. The working gas crosses the internal passage between the cold mouth and the cold orifice so as to be transferred to exchanger 6 to be heated. At the same time, no mouth of the low pressure bushel communicates with a light from the cylinder head. The synchronization of the high pressure plug with respect to the ascent of the piston during compression is adjusted so as to limit an unfavorable phenomenon of relatively high pressure in the working chamber.
    With reference to FIG. 2b, the synchronization of the piston 3 and of the plugs 20, 30 is such that the piston 3 is located in top dead center while the rotation of the high pressure plug 20 allows a double circulation of working gas to the inside the latter. The cold mouth 21 of the high-pressure plug 20 coincides at least partially with the same lumen of the cylinder head as previously, and simultaneously the cold orifice 23 coincides at least partially with the same lumen of a connection of the cold end B of exchanger 6, than previously. An internal so-called cold passage from the high-pressure plug allows the working gas to be transferred from the working chamber to the exchanger 6, via the cold end B. In addition, the synchronization allows a hot mouth 22 to coincide with the at least partially with the same lumen as for the cold mouth 21, and simultaneously allows a hot orifice 24 to coincide at least partially with a lumen of a connection of the hot end C of the exchanger 6. An internal passage says hot, distinct from the internal cold passage, allows the working gas to be transferred from the exchanger 6, via the hot end C, to the working chamber 5.
    A communication between the cold end B and the hot end C of the exchanger is then established so that part of the incoming working gas and part of the outgoing working gas comes into contact. Working gas still passes through the internal passage between the cold opening and the cold opening, and working gas passes through the internal passage between the hot opening and the hot opening. The volume of gas previously compressed is in fact distributed in the path between the cold end B and the hot end C of the exchanger 6, the working gas being heated thanks to the heat transfer fluid present in the heat-yielding path 61 of the exchanger 6. Simultaneously, no mouth of the low pressure plug communicates with a light from the cylinder head.
    Afterwards, the heated working gas leaving the high pressure valve expands in the working chamber. With reference to FIG. 2c, the synchronization of the piston 3 and of the bushels 20, 30 is such that the movement of the piston 3 is descending while the rotation of the high pressure bushel 20 allows the hot mouth 22 of the high pressure bushel to communicate with the same light from the cylinder head as previously and simultaneously allows a hot orifice 24 to communicate with the same light, as previously, from a connection of the hot end C of the exchanger 6. The working gas passes through the passage internal between the hot orifice 24 and the hot mouth 22 so as to be transferred from the exchanger 6 to the working chamber to be relaxed. At the same time, no mouth of the low pressure bushel communicates with a light from the cylinder head. Once the piston has reached bottom dead center, no high pressure valve mouth communicates with a cylinder head lumen.
    With reference to FIG. 1b, an exhaust phase of the working gas is illustrated. The synchronization of the piston 3 and of the plugs 20, 30 is such that the movement of the piston 3 is rising while the rotation of the low pressure plug 30 allows an exhaust outlet 31 of the low pressure plug to communicate with a light from the cylinder head and simultaneously allows an exhaust port 33 to communicate with a lumen of an exhaust fitting. The working gas passes through the internal passage between the exhaust mouth 31 and the exhaust orifice 33 so as to be expelled from the working chamber 5. At the same time, no mouth of the high pressure plug communicates with a light of the breech. The working gas is released into the outside environment. When the piston has reached top dead center, the low pressure plug has pivoted so that the exhaust mouth 31 of the low pressure plug no longer communicates, even partially, with a cylinder head lumen (apart from any delay in admission closing ).
    Preferably, the exhaust fitting and the inlet fitting form a single piece comprising at least one inlet for the inlet and at least one outlet for the exhaust, each of the resources being transferred into a respective conduit. For the rest, an exhaust connection and / or an intake connection can be called either a so-called "low pressure" connection.
    Thanks to the bushel, the transfers of the working gas are brief and take place through a passage section large enough to minimize the pressure losses. In addition, as the thermodynamic cycle can be carried out in a single cylinder, the engine has a very small footprint compared to the external hot source engine of the prior art.
    We will now describe a specific embodiment, which will be described in these differences from the above embodiment. According to one embodiment, there is provided an external hot source engine comprising two cylinders.
    Referring to Figure 3, there is shown a cylinder head 4 arranged and configured to be installed on an external hot source engine comprising two cylinders arranged in a so-called "in-line" arrangement.
    The cylinder head 4 is then provided to overcome an engine block in which two cylinders are formed. It has a lower face 46 and two lateral faces (not visible in FIG. 3) provided to support the high pressure valve and the low pressure valve respectively, which are arranged parallel to each other.
    The underside 46 is substantially flat and is intended to be in contact with the jacket of the engine. It comprises two chamber openings 46a, 46b, each chamber opening being provided to coincide with a cylinder of the engine. Each chamber opening 46a, 46b defines an inlet for a transition cavity 45 hollowed out inside the cylinder head. The transition cavity 45 has a substantially triangular shape and is, in operation, opposite the working chamber. Preferably, the piston head has a shape complementary to the shape of the transition cavity, so that the head can enter the transition cavity. When the engine is running, the volume of the cavity extends the volume of the working chamber.
    According to the embodiment shown in Figure 3, the cylinder head includes eight lights, four lights being provided per cylinder (four on the left and four on the right of Figure 3) to circulate the working gas according to the phases described above.
    For a cylinder, two so-called “high pressure” lights 41hp are provided for circulating the gas towards the high pressure bushel and vice versa, and two so-called “low pressure” lights 41bp are provided for circulating the working gas to the low pressure bushel and vice versa. The 41hp high pressure lights are produced on the same first side face of the cylinder head. The low pressure ports 41bp are produced on the same lateral face of the cylinder head opposite the first face; the four lights opening into a transition cavity.
    Referring to Figure 4, there is shown a high engine arranged and configured to be installed on a jacket of an external hot source engine comprising two cylinders arranged in a so-called "in-line" arrangement. The high engine comprises a cylinder head 4, in accordance with FIG. 3, on which is mounted a low pressure plug 30, only one end of which is visible in FIG. 4. The low pressure plug is covered with a low pressure connection 70 which will be described in more detail below. The cylinder head 4 has on a side face a receiving surface 40 on which a rotary plug, here the high pressure plug 20, can be received. The receiving surface 40 has a concave shape, so as to cooperate by complementary shape with the high pressure plug 20. In particular the receiving surface has a section in the form of an arc of a circle substantially coaxial with the axis of the received plug. . The arrangement of the cylinder head 4 is substantially symmetrical as regards the shape of the lateral faces. The high pressure bushel like the low pressure bushel has, according to a cross section, a circular external shape. In addition, the two bushels have a substantially identical diameter.
    According to the embodiment shown in Figure 4, the receiving surface 40 comprises four high pressure lights 41hp: two pairs of lights 41a, 41b adjacent, each couple being provided to cooperate with a cylinder. Preferably, the lights have a rectangular shape to limit the pressure losses during the circulation of the working gas flow.
    FIG. 4 shows the high pressure plug in a particular angular position when the synchronization of the engine is such that:
    - for one of the cylinders, called “cylinder a”, the working gas undergoes a compression phase, and
    - for the other cylinder, called "cylinder b", the working gas undergoes an expansion phase.
    In this particular position, no working gas circulates in internal passages of the high pressure plug 20.
    Referring to Figures 4, 5a, 6a, the cylinder head 4 comprises two slots 41a provided to overcome the cylinder a, and two slots 41b provided to overcome the cylinder b. The high pressure plug 20 comprises two adjacent cold mouths 21a, of identical dimensions and aligned on the periphery of the plug, along a direction parallel to the axis of rotation of the plug. The cold mouths have a substantially rectangular shape whose longitudinal dimension extends in a direction which is parallel to the axis of rotation of the plug. The cold mouths 21a are intended to coincide with the lights 41a of the cylinder head so that the working gas can circulate from the working chamber of the cylinder a towards the high pressure valve 20. At the other end of the internal passage and in reference in Figure 4, there is a cold orifice 23a arranged at the periphery of the high pressure plug. The two cold mouths 21a on the one hand, and the cold orifice 23a on the other hand, respectively define the two ends of the internal passage used to circulate the working gas towards the cold end of the exchanger. The orifice 23a is intended to coincide with a lumen 63a of the high pressure fitting 60. The orifice 23a has a rectangular shape whose longitudinal dimension extends in a direction which is orthogonal to the axis of rotation of the plug.
    In addition, the openings 41 are spaced from each other so that the orifices (cold and hot) are opposite the receiving surface 40 of the cylinder head 4 between two openings. Preferably, the spacing between two transverse edges of two adjacent openings is equal to or greater than the transverse dimension of an orifice. The orifices are therefore dimensioned as a function of the spacing between two lumens, or of the spacing between a lumen and the axial end of the receiving surface. Thus, for example, the cold orifice 23a is aligned circumferentially with the circumferential surface separating the two cold mouths 21a.
    With reference to FIG. 4, it can also be distinguished that the high pressure plug comprises two adjacent hot mouths 22a, of identical dimensions and aligned on the periphery of the plug, along a direction parallel to the axis of rotation of the plug. The hot mouthpieces have a substantially rectangular shape whose longitudinal dimension extends in a direction which is parallel to the axis of rotation of the plug. The hot mouths 22a are circumferentially aligned with the cold mouths 21a. The hot mouths 22a are intended to coincide with the openings 41a of the cylinder head so that the working gas can circulate from the high pressure valve 20 to the working chamber of the cylinder a. In addition, the hot mouths 22a and the cold mouths 21a are spaced along the circumference of the plug with a very small angular movement, for example 5 to 15 degrees. The angular movement is chosen so that a light 41 can communicate simultaneously with a cold mouth and a hot mouth.
    For example, each hot mouth has, along the circumference of the plug, an angular opening of between 20 and 50 degrees, preferably between 25 and 35 degrees. Given that the engine performs four main phases and that the internal passages are separated by walls of non-zero thickness, these values are chosen according to a compromise between the need for a large passage section of the working gas flow, reduction of pressure losses and size (diameter and length of the plug). Each cold mouth has, along the circumference of the plug, an angular opening of, for example, between 10 and 40 degrees, preferably between 20 and 30 degrees.
    In addition, each light 41hp has, along the circumference of the reception surface 40, an angular opening of, for example, between 15 and 30 degrees.
    Preferably, the orifices have, along the circumference of the plug, an angular opening of between 100 and 350 degrees, preferably between 120 and 150 degrees.
    Regarding the cylinder b and according to the particular angular position of the high pressure plug, the synchronization of the engine is such that no mouth communicates with the lights 41b of the cylinder head. With reference to FIG. 4, it can be distinguished in part that the high pressure plug comprises a cold orifice 23b intended to coincide with a lumen 63b of the high pressure connector 60 so that the working gas coming from the working chamber of the cylinder b can circulate from the high pressure valve to the high pressure fitting. It can also be seen that the high pressure plug comprises two hot orifices 24b intended to communicate respectively with two ports of the high pressure connection 60 so that the working gas coming from the hot end of the exchanger can circulate from the high pressure connection ( via two lights (one light 65 and another light not visible) towards the high pressure valve intended for the working chamber of the cylinder b. The high pressure fitting 60 has a covering surface 69 arranged and configured to cooperate by complementary shape with the peripheral surface left free by the cylinder head 4. The covering surface 69 has, in a cross section, a shape substantially in an arc .
    Between the part of the high pressure valve selectively communicating with the cylinder a and the part of the high pressure valve selectively communicating with the cylinder b, the mouths and orifices are respectively diametrically opposed.
    We will now describe with reference to Figures 5a, 5b, 6a and 6b the angular positions of the high pressure valve 20 when the working gas flows between the working chamber of the cylinder b and the exchanger. FIG. 5a shows the high pressure plug in a particular angular position when the synchronization of the engine is such that:
    - for cylinder a, the working gas undergoes an exhaust phase, which will be described below, and
    - for cylinder b, the compressed working gas and / or during compression is transferred to the cold end of the exchanger (also visible in Figure 5b).
    With reference to FIG. 5a, the high pressure plug 20 comprises two cold mouths 21b seen in transparency from the circumference of the plug and conforms to the cold mouths of FIG. 4. The two cold mouths 21b form the entrance to the internal passage, also seen in transparency, up to a cold opening 23b. Said internal passage comprises two conduits extending respectively from a cold mouth 21b, then the two conduits meet towards a common conduit, thus forming the internal passage between the two cold mouths 21b and the cold orifice 23b. The synchronization of the engine is such that the cold mouths 21b communicate with the lights 41b of the cylinder head so that the working gas circulates from the working chamber of the cylinder b towards the high pressure valve, and simultaneously the cold orifice 23b, conforming at the cold orifice of FIG. 4, communicates with the lumen 63b of the high pressure connection 60 so that the working gas circulates from the high pressure valve to the high pressure connection. With reference to FIG. 5b, the cold mouth 21b coincides perfectly with the lumen 41b of the cylinder head, and the cold orifice 23b coincides perfectly with the lumen 63b of the high pressure fitting. The gas, which has been previously compressed in the working chamber by the rise of the piston 3, is pushed back into the internal passage of the high pressure plug 20.
    In addition, one can also distinguish in part two hot orifices 24a intended to communicate respectively with two ports of the high pressure connection 60 so that the working gas coming from the hot end of the exchanger can circulate from the high pressure connection ( via two lights, a light 64a and a light 65) towards the high pressure valve 20 intended for the working chamber of the cylinder a.
    With reference to FIGS. 6a and 6b, the angular position of the high pressure plug is such that said plug has turned a few degrees anticlockwise, so that the working gas flows from the hot end of the exchanger to the cylinder working chamber b. FIG. 6a shows the high pressure plug in a particular angular position when the synchronization of the engine is such that:
    - for cylinder a, the working gas undergoes an exhaust end phase, which will be described below, and
    - for cylinder b, the working gas leaves the hot end of the exchanger and is transferred to the working chamber of cylinder b to be expanded (also visible in Figure 6b).
    With reference to FIG. 6a, the high pressure plug 20 comprises two hot orifices 24b conforming to the orifices of FIG. 4. Each hot orifice 24b forms an inlet of an internal passage, seen in transparency from the circumference of the plug, up to a hot mouth 22b, the two hot mouths also being seen in transparency from the periphery of the plug. Each internal passage leads the working gas in parallel and communicates respectively and simultaneously with a light from the cylinder head. The working gas flow is divided into two flow lines which circulate in two separate internal passages inside the plug. The two flow lines are divided before entering the two orifices 24b of the high pressure plug and join after the exit of the two ports 41b of the cylinder head. This characteristic makes it possible to propose a large cross section for the flow of working gas.
    The synchronization of the engine is such that the hot orifices 24b communicate with lights (light 65 and a second light not visible) from the high pressure connection 60 so that the working gas circulates from the hot end of the exchanger to the high pressure bushel 20, and simultaneously the hot mouths 22b, in accordance with the hot mouths of FIG. 4, communicate with the ports 41b of the cylinder head so that the working gas circulates from the high pressure bushel to the working chamber of the cylinder b. With reference to FIG. 6b, the hot mouth 22b perfectly coincides with the lumen 41b of the cylinder head, and the hot orifice 24b perfectly coincides with the lumen 65 of the high pressure fitting 60. The gas, which has been previously heated in the 'exchanger, is expanded in the working chamber of the cylinder b so as to push the piston 3 in a downward movement.
    During engine operation and with reference to the cycle described above, the cold and compressed working gas and / or being compressed enters the high pressure valve 20 in rotation as soon as at least part of the two cold mouths 21b communicates with the lights 41b so as to circulate the cold and compressed working gas towards the cold end of the exchanger. The passage section between the working chamber and the cold mouths increases with the rotation of the high pressure plug. When the cold mouths of the high pressure bushel perfectly coincide with the cylinder head lights, the passage section is maximum. Most of the volume of cold, compressed working gas has passed through said mouths. Then, due to the rotation of the high pressure bushel and the end of the compression, only part of the mouths communicates with the ports, so as to circulate the remaining part of the cold and compressed working gas towards the cold end of the exchanger. Simultaneously, the passage section between the working chamber and the hot mouths increases so that a part of said hot mouths communicates with the same light. The working gas leaving the hot mouths, and therefore entering the working chamber, comes from the hot end of the exchanger after being heated. The working gas thus makes a loop passing through the same lights of the cylinder head but through different internal passages of the high pressure bushel. For a short time the cold working gas and the hot working gas intersect.
    According to a particular embodiment of the high pressure valve provided for an engine comprising two cylinders, the high pressure valve 20 has two orifices circumferentially aligned to communicate selectively with the high pressure connector. With reference to FIG. 5a, one of the hot orifices 24a, intended to carry out the communication of the working gas coming from the cylinder a, and one of the hot orifices 24b, intended to carry out the communication of the working gas coming from the cylinder b, are aligned circumferentially. Said orifices are arranged substantially in the center of the plug and are 180 degrees opposite. The internal passages upstream of said orifices are adjoining and have a common wall. During operation of the engine, each of said two orifices successively communicates a passage associated with a port 65 of the high pressure connection. This characteristic makes it possible to reduce the size of the plug and therefore the size of the motor.
    We will now describe with reference to FIGS. 7a, 7b, 8a and 8b the angular positions of the low pressure plug 30 when the working gas circulates between the working chamber of one of the cylinders and a low pressure fitting 70.
    Referring to Figures 7a and 8a, there is shown a high engine similar to Figures 4, 5a and 5b. Only the low pressure part of the high engine will be described since the high pressure part of the high engine is identical to Figures 4, 5a and 5b. As for the high pressure part, the side face receiving the low pressure plug has a receiving surface 40 comprising four low pressure ports 41bp: two pairs of adjacent ports 41a, 41b being provided to cooperate respectively with a cylinder a and a cylinder b.
    FIG. 7a shows the low pressure plug in a particular angular position when the synchronization of the motor is such that:
    - for cylinder a, working gas is admitted into the working chamber (intake phase), and
    - for cylinder b, the working gas undergoes an expansion phase.
    In this particular position, no working gas circulates in internal passages of the high pressure plug.
    With reference to FIGS. 7a, 8a, the cylinder head 4 comprises openings 41a intended to overcome the cylinder a, and openings 41b provided to overcome the cylinder b. The low pressure plug 30 comprises two adjacent inlet mouths 32a (not visible in FIGS. 7a), of identical dimensions and aligned on the periphery of the plug, along a direction parallel to the axis of rotation of the plug. The inlet mouths 32a have a substantially rectangular shape whose longitudinal dimension extends in a direction which is parallel to the axis of rotation of the plug. According to the angular position represented by FIG. 7a, the inlet mouths 32a communicate with the two openings 41a of the cylinder head 4 so that the working gas circulates from the low pressure valve 30 to the working chamber of the cylinder a. At the other end of the internal passage and with reference to FIGS. 7a and 7b, there is an intake orifice 34a arranged at the periphery of the low pressure plug (partially visible in FIG. 8a). The two inlet mouths 32a on the one hand, and the inlet orifice 34a on the other hand, respectively define the two ends of the internal passage used to circulate the working gas from the low pressure fitting 70 to the chamber working cylinder a. Depending on the angular position shown, the inlet orifice 34a communicates with an inlet port 74a of the low pressure fitting 70.
    During operation, the outside air, serving as working gas, is introduced into the low pressure fitting via an inlet inlet 71. The inlet orifice 34a has a rectangular shape whose longitudinal dimension extends in a direction which is orthogonal to the axis of rotation of the plug.
    With reference to FIG. 7b, an inlet mouth 32a coincides perfectly with a port 41a of the cylinder head, and the inlet orifice 34a coincides perfectly with the port 74a of the low pressure fitting 70. The downward movement of the piston 3 allows working gas inlet, see arrow fA.
    Furthermore with reference to FIGS. 7a and 8a, each pair of lights 41bp is spaced from an axial end 49 of the reception surface 40 so that the intake orifices are opposite the reception surface 40 of the cylinder head 4 between an axial end 49 of the receiving surface 40 and a transverse edge 39 of a lumen 41bp of the cylinder head. Preferably, the spacing between an axial end 49 of the receiving surface 40 and a transverse edge 39 is equal to or greater than the transverse dimension of an inlet orifice.
    With reference to FIGS. 7a and 8a, it can also be distinguished that the low pressure plug 30 comprises two adjacent exhaust mouths 31a, of identical dimensions and aligned on the periphery of the plug, along a direction parallel to the axis of rotation of the bushel. The exhaust mouths 31a have a substantially rectangular shape whose longitudinal dimension extends in a direction which is parallel to the axis of rotation of the plug. The exhaust mouths 31a are circumferentially aligned with the intake mouths 32a. The exhaust mouths 31a are intended to communicate with the lights 41a of the cylinder head so that the working gas can circulate from the working chamber of the cylinder a to the low pressure valve 30 via an internal passage. At the opposite end of the exhaust mouths 31a, the internal passage opens out through an exhaust orifice 33a. In addition, the exhaust mouths 31a and the inlet mouths 32a are spaced along the circumference of the plug with a small angular movement, for example, from 100 to 350 degrees, preferably from 200 to 250 degrees.
    Preferably, each exhaust mouth has, along the circumference of the low pressure valve, an angular opening of between 70 and 100 degrees, preferably between 80 and 90 degrees. In addition, each inlet mouth has, along the circumference of the plug, an angular opening comprised, for example, between 70 and 100 degrees, preferably between 80 and 90 degrees.
    In addition, each light 41bp has, along the circumference of the reception surface 40, an angular opening of, for example, between 40 and 100 degrees.
    Preferably, the intake and exhaust ports have, along the circumference of the plug, an angular opening of between 30 and 60 degrees, preferably between 40 and 55 degrees.
    Between the part of the low pressure valve selectively communicating with the cylinder a and the part of the low pressure valve selectively communicating with the cylinder b, the mouths and orifices are respectively diametrically opposite according to the embodiment shown.
    Regarding the cylinder b and according to the particular angular position of the low pressure plug, the synchronization of the engine is such that no mouth coincides with the ports 41b of the cylinder head. With reference to FIG. 7a, it can be seen that the low pressure valve comprises two inlet mouths 32b intended to communicate with two ports 41b so that the working gas coming from the low pressure connector 70 can circulate from the low pressure valve (in passing through an inlet orifice 34b not visible in FIG. 7a) towards the working chamber of the cylinder b. A distinction is also made in part that the low pressure plug 30 comprises two exhaust mouths 31b intended to communicate respectively with the two ports 41b of the cylinder head 4 so that the working gas can flow from the working chamber of the cylinder b towards the low pressure connection 70. It is further distinguished that the low pressure valve 30 comprises an exhaust orifice 33b. The exhaust mouths 31b on the one hand, and the exhaust orifice 33b on the other hand correspond to the two ends of the internal passage making it possible to circulate the working gas coming from the working chamber of the cylinder b towards the fitting low pressure.
    FIG. 8a shows in particular the angular position of the low pressure plug 30 when working gas is escaped from the working chamber of cylinder b. With reference to FIG. 8a, the two exhaust mouths 31b of the low pressure plug 30 are seen in transparency from the circumference of the plug and in accordance with the exhaust mouths of FIG. 7a. The two exhaust mouths 31b form the entrance to the internal passage, also seen in transparency, up to the exhaust orifice 33b. The synchronization of the engine is such that the exhaust mouths 31b communicate with the ports 41b of the cylinder head 4 so that the working gas circulates from the working chamber of the cylinder b to the low pressure valve, and simultaneously the orifice d 'exhaust 33b, conforming to the exhaust port of Figure 7a, communicates with the lumen 75 of the low pressure fitting 70 so that the working gas flows from the low pressure valve to the low pressure fitting. Referring to Figure 8b, the exhaust mouth 31b coincides perfectly with the lumen 41b of the cylinder head, and the exhaust port 33b coincides perfectly with the lumen 75 of the low pressure fitting. The movement of the piston 3 is such that the working gas is pushed back into the internal passage of the low pressure plug 30 then towards the low pressure fitting 70, see arrow fD.
    With reference to FIGS. 7a and 8a, the exhaust orifices 33a and 33b are aligned circumferentially along the periphery of the low pressure plug 30. Said orifices are opposite for example by 180 degrees and the internal passages upstream of said orifices are adjoining and have a common wall. During engine operation, each orifice successively communicates an internal passage associated with a single exhaust port 75 of the low pressure fitting. This characteristic makes it possible to reduce the size of the plug and therefore the size of the motor.
    In addition, each pair of lights 41bp is spaced from one another along the receiving surface 40 so that the exhaust orifices are facing the receiving surface 40 of the cylinder head 4 separating the pair of light 41a of the pair of light 41b. Preferably, the spacing between the two pairs of lights is equal to or greater than the transverse dimension of an exhaust orifice.
    权利要求:
    Claims (17)
    [1" id="c-fr-0001]
    1. External hot source motor (1) comprising:
    - at least one cylinder (2),
    - a piston (3) movable back and forth in the cylinder (2),
    - a cylinder head (4) defining, with the piston (3) and the cylinder (2), a working chamber (5) for a working gas,
    - a distribution mounted in the cylinder head (4) and selectively communicating the working chamber (5) with the following resources:
    o an inlet (A) for working gas, o a cold end (B) of a heat exchanger (6), o a hot end (C) of the heat exchanger (6), o an exhaust (D ), characterized in that the distribution comprises at least one rotary plug (20, 30) rotatably mounted in the cylinder head (4) and having internal passages opening out through its side wall by at least one mouth (21, 22; 31 , 32) which selectively communicates with the working chamber (5) by at least one light (41) formed in the cylinder head (4).
    [2" id="c-fr-0002]
    2. Engine (1) according to claim 1, characterized in that at least one lumen (41) of the cylinder head is capable of communicating with two internal passages of the plug which open out through the side wall of the plug via two openings (21 , 22; 31, 32) aligned circumferentially.
    [3" id="c-fr-0003]
    3. Motor (1) according to claim 2, characterized in that said two internal passages are, one, a passage through which the working gas enters the working chamber (5), and the other, a passage by which the working gas leaves the working chamber (5).
    [4" id="c-fr-0004]
    4. Motor (1) according to one of claims 1 to 3, characterized in that at the end opposite the mouths (21, 22; 31, 32), the internal passages open out through the side wall of the plug ( 20, 30) by orifices (23, 24; 33, 34) which selectively communicate with fixed connections (60, 70) according to the angular position of the plug.
    [5" id="c-fr-0005]
    5. Motor (1) according to claim 4, characterized in that, for each passage, the geometry of the at least one bushel (20, 30) is such that the orifice (23, 24; 33, 34) is capable of communicating with the corresponding fitting (60, 70) when the mouth (21, 22; 31, 32) communicates with the working chamber (5).
    [6" id="c-fr-0006]
    6. Motor (1) according to claim 4 or 5, characterized in that, on the at least one plug (20, 30), the at least one mouth (21, 22; 31, 32) is axially offset by relative to the at least one orifice (23, 24; 33, 34).
    [7" id="c-fr-0007]
    7. Motor (1) according to one of claims 1 to 6, characterized in that the at least one bushel comprises a low pressure bushel (30) controlling the selective communication of the working chamber (5) with the intake (A) and the exhaust (D).
    [8" id="c-fr-0008]
    8. Motor (1) according to one of claims 1 to 7, characterized in that the at least one bushel comprises a high pressure bushel (20) controlling the selective communication of the working chamber (5) with the hot ends (C) and cold (B) of the exchanger (6).
    [9" id="c-fr-0009]
    9. Motor (1) according to claim 8, characterized in that the distribution is arranged so that, towards the end of the compression, the working chamber (5) begins to communicate with the cold end (B) of the 'exchanger (6) when the pressure in the working chamber is lower than the pressure in the exchanger (6).
    [10" id="c-fr-0010]
    10. Motor (1) according to one of claims 1 to 9, characterized in that the at least one mouth comprises two mouths (21, 22; 31, 32), for the same passage, capable of communicating simultaneously with the working chamber (5), by two lights (41).
    [11" id="c-fr-0011]
    11. Engine (1) according to one of claims 1 to 10, characterized in that at least one passage comprises two passages leading in parallel to the same resource, capable of simultaneously communicating each with a light (41) of the cylinder head.
    [12" id="c-fr-0012]
    12. Motor (1) according to one of claims 1 to 11, having at least two cylinders, characterized in that the at least one plug (20, 30) has two orifices circumferentially aligned to communicate selectively with the same fitting, and which each communicate with a respective passage associated with a respective one of the cylinders.
    [13" id="c-fr-0013]
    13. Motor (1) according to one of claims 1 to 12, characterized in that the openings (41) are surrounded by a sealing device to close the gap between the peripheral wall of the plug and an adjacent surface of the cylinder head all around each light (41).
    [14" id="c-fr-0014]
    14. Motorization assembly comprising a motor (1) according to one of claims 1 to 13 and a heat exchanger (6) having a heat-receiving path (62) extending between cold end (B) and a hot end (C ) selectively connected to the working chamber (5) towards the end of a compression phase and towards the start of an expansion phase, respectively.
    [15" id="c-fr-0015]
    15. The assembly of claim 14, characterized in that the heat exchanger (6) is of the counter-current type.
    [16" id="c-fr-0016]
    16. An assembly according to claim 14 or 15, characterized in that the heat exchanger (6) comprises a heat transfer path (61) traversed by the exhaust gases of an internal combustion engine.
    [17" id="c-fr-0017]
    17. The assembly of claim 14 or 15, characterized in that the heat exchanger (6) comprises a heat transfer path (61) traversed by a fluid heated with solar energy.
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    同族专利:
    公开号 | 公开日
    CN111108285A|2020-05-05|
    WO2019025555A1|2019-02-07|
    US20200240297A1|2020-07-30|
    EP3662153A1|2020-06-10|
    FR3069884B1|2020-02-21|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US20060213207A1|2005-03-25|2006-09-28|Redlich Robert W|Reciprocating four-stroke Brayton refrigerator or heat engine|
    US20080148731A1|2006-12-22|2008-06-26|Yiding Cao|Heat engines|
    EP2816013A2|2008-10-02|2014-12-24|BAUDINO, Etienne|Motorised hybrid system comprising a combination of two complementary engine cycles|WO2021123351A1|2019-12-20|2021-06-24|H2P Systems|Gate valve composed of two coaxial portions, and motor with external heat source comprising same|
    WO2021123358A1|2019-12-20|2021-06-24|H2P Systems|Split-cycle external heat source engine with slide valves|WO2006099064A2|2005-03-09|2006-09-21|Zajac Optimum Output Motors, Inc.|Internal combustion engine and method with improved combustion chamber|
    FR2905728B1|2006-09-11|2012-11-16|Frederic Thevenod|HYBRID ENGINE WITH EXHAUST HEAT RECOVERY|
    FR2954799B1|2009-12-28|2012-10-19|Frederic Olivier Thevenod|EXTERNAL HOT SOURCE THERMAL MACHINE, POWER GENERATION GROUP AND VEHICLE THEREOF.|RU2749241C1|2020-04-21|2021-06-07|Владимир Викторович Михайлов|Engine with external heat supply and method of operation of an engine with external heat supply|
    法律状态:
    2019-02-08| PLSC| Search report ready|Effective date: 20190208 |
    2019-08-29| PLFP| Fee payment|Year of fee payment: 3 |
    2020-08-27| PLFP| Fee payment|Year of fee payment: 4 |
    2021-08-27| PLFP| Fee payment|Year of fee payment: 5 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1757398|2017-08-02|
    FR1757398A|FR3069884B1|2017-08-02|2017-08-02|EXTERNAL HOT SOCKET MOTOR|FR1757398A| FR3069884B1|2017-08-02|2017-08-02|EXTERNAL HOT SOCKET MOTOR|
    US16/635,616| US20200240297A1|2017-08-02|2018-08-02|External heat source engine with slide valves|
    EP18758546.8A| EP3662153A1|2017-08-02|2018-08-02|External heat source engine with slide valves|
    CN201880055168.9A| CN111108285A|2017-08-02|2018-08-02|External heat source engine with slide valve|
    PCT/EP2018/071017| WO2019025555A1|2017-08-02|2018-08-02|External heat source engine with slide valves|
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