EP4077902A1 - Moteur a source chaude externe a cycle divise a boisseaux - Google Patents
Moteur a source chaude externe a cycle divise a boisseauxInfo
- Publication number
- EP4077902A1 EP4077902A1 EP20838061.8A EP20838061A EP4077902A1 EP 4077902 A1 EP4077902 A1 EP 4077902A1 EP 20838061 A EP20838061 A EP 20838061A EP 4077902 A1 EP4077902 A1 EP 4077902A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- working chamber
- plug
- low temperature
- valve
- high temperature
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 239000007789 gas Substances 0.000 claims description 120
- 238000009826 distribution Methods 0.000 claims description 35
- 238000004891 communication Methods 0.000 claims description 16
- 230000002093 peripheral effect Effects 0.000 claims description 16
- 230000006835 compression Effects 0.000 claims description 9
- 238000007906 compression Methods 0.000 claims description 9
- 238000002485 combustion reaction Methods 0.000 claims description 4
- 238000007789 sealing Methods 0.000 claims description 4
- 239000013529 heat transfer fluid Substances 0.000 description 5
- 238000010276 construction Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 4
- 230000000295 complement effect Effects 0.000 description 3
- 230000001360 synchronised effect Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 1
- 239000003344 environmental pollutant Substances 0.000 description 1
- 230000000763 evoking effect Effects 0.000 description 1
- 231100000719 pollutant Toxicity 0.000 description 1
- 238000005482 strain hardening Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G1/00—Hot gas positive-displacement engine plants
- F02G1/02—Hot gas positive-displacement engine plants of open-cycle type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
- F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
- F02G5/02—Profiting from waste heat of exhaust gases
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a split-cycle external hot-source engine comprising a pair of cylinders, a low-temperature cylinder and a high-temperature cylinder, each comprising a reciprocating movable piston and respectively defining with each of them a working chamber. low temperature and a high temperature working chamber for a working gas.
- a distribution mounted in the cylinder head selectively communicates, on the one hand the low temperature working chamber with a working gas inlet and a cold end of a heat exchanger, and on the other hand the high temperature working chamber with a hot end of the heat exchanger and an exhaust.
- the distribution comprises at least one rotary valve comprising at least one internal passage associated with each working chamber, so as to conduct the working gas between the working chambers and the resources.
- External hot source engines 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 works between two heat sources external to the engine through exchangers. It uses valves to control the flow of working fluid (in gas phase) between two chambers, one for compression and the other for expansion.
- valves actuated by cams For positive-displacement 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 to the working chamber must be low. In addition, the maximum valve lift is low if the duration (measured in degrees of cam angle of rotation) of opening the valve is short. In addition, the cam drive consumes energy. Positive displacement machines are also known, such as compressors, which use a valve distribution. This solution requires that the pressure differential on each valve always have, at each stage of the operating cycle of the machine, an appropriate value and direction so that the valve is in the state - open or closed - necessary for the considered stage of the operation. cycle.
- Patent application FR 3 069 884 discloses an external hot source motor comprising plugs.
- Each plug is rotatably mounted 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 slot made in the cylinder head.
- Each bushel is made in one piece. The plug offers a larger passage section for the working gas and reduces pressure losses.
- the object of the present invention is to propose an external hot-source motor making it possible to remedy at least in part the problems mentioned above. Disclosure of the invention
- an external hot source engine comprising:
- a cylinder head defining, o with the low temperature piston and the low temperature cylinder, a low temperature working chamber for a working gas, and o with the high temperature piston and the high temperature cylinder, a high temperature working chamber for the working gas,
- a distribution mounted in the cylinder head and selectively communicating o the low temperature working chamber with the following resources: a working gas inlet and a cold end of a heat exchanger, and o the high temperature working chamber with the following resources: a hot end of the heat exchanger and an exhaust.
- the distribution comprises at least one rotary valve mounted in rotation in the cylinder head.
- the at least one rotary valve has at least one internal passage associated with each working chamber, each internal passage opening through the side wall of the at least one rotary valve via at least one mouth, each mouth selectively communicating with a chamber working by at least one light made in the cylinder head.
- Internal passages conduct the working gas between the working chambers and the resources.
- the engine according to the invention makes it possible, compared to the external hot-source engines of the prior art, in particular with a single cylinder, to distribute gas flows with less heat loss and little pressure drop.
- the engine according to the invention has the advantage of facilitating the flow of gases due to the natural spacing between the cylinders.
- the proposed motor thus offers better efficiency.
- the valve distribution system makes it possible to provide a large cross section for the passage of the working gas, in particular as soon as a mouthpiece begins to coincide with a lumen in the cylinder head.
- the passage section increases rapidly, for example linearly, until the mouthpiece coincides perfectly with the lumen of the breech.
- a cam actuates a valve according to a substantially sinusoidal law so that the working gas passage section increases very slowly at the start of the opening movement.
- a distribution comprising at least one valve makes it possible to limit the friction with respect to valve distributions, and makes it possible to reduce the acyclism of the crankshaft.
- thermodynamic cycle of the four-stroke type, as follows:
- the at least one bushel includes:
- the working gas entering the exchanger is said to be “cold” by comparison with its higher temperature when it exits the exchanger “hot”. However, it must 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.
- the two aforementioned transfers of the working gas are brief and take place through a sufficiently large and rectilinear passage section to minimize pressure drops.
- the engine of the present invention requires two working chambers, a low temperature working chamber and a high temperature working chamber, in order to carry out the four-stroke thermodynamic cycle.
- hot gas relative to cold gas is understood to mean a hot gas which has a higher temperature than that of a cold gas.
- cold are understood to mean a relative meaning simply that a hot element, for example a hot mouthpiece or a hot orifice, is generally hotter than a cold element, for example. a cold mouthpiece or a cold orifice, when the engine is running.
- plug is understood to mean a cylindrical element comprising internal passages in which the working gas can circulate.
- An internal passage is for example a duct.
- the at least one plug is arranged so that its axis of rotation is perpendicular to the axis of the cylinders above which it is arranged.
- the at least one bushel is located between the working chambers and an exchanger along the working gas path. The rotary movement of the at least one bushel is synchronized with the reciprocating movement of the pistons, so that the working gas can pass through the at least one bushel via the internal passages, and thus distribute the gas between the working chambers and the exchanger.
- each internal passage communicates with at least two openings made through the side wall of the valve, each opening being located at one of the two ends of the internal passage.
- each internal passage has an opening, called a mouth, and at a second end, each internal passage has an opening, called an orifice.
- the working gas flows between the low temperature working chamber and the cold inlet of the exchanger passing through at least one lumen of the cylinder head, at least one mouth and at least one orifice. at least one internal passage of the plug. Then the working gas flows between the hot outlet of the exchanger and the high temperature working chamber passing through at least one orifice and at least one mouth of at least one internal passage of the plug and at least one lumen of the cylinder head.
- each internal passage comprises at least one mouth.
- An orifice is called an opening located at another end of the internal passage of the plug.
- the orifice is located opposite the mouth.
- the terms mouthpiece and orifice correspond to, or qualify, openings made through the side wall of the plug.
- the term mouthpiece is used to qualify each opening capable of communicating with the lumen of the breech for the passage of the working gas between a working chamber and a plug or vice versa.
- a mouth is always made through the peripheral wall of the plug, also called the circumferential wall.
- orifice is used to describe each opening capable of communicating with a fitting for the passage of working gas from the plug to the fitting or vice versa.
- An orifice can be made through the peripheral wall of the plug, also called the circumferential wall, or through the transverse wall of the plug.
- a mouthpiece cannot be used as an orifice and vice versa.
- the at least one mouth is offset axially with respect to the at least one orifice.
- side wall is meant, by evoking a plug, on the one hand a peripheral wall, also called the circumferential wall, which extends along a face cylindrical of the plug, or on the other hand a transverse wall, also called the axial face of the plug, which extends along a planar face thereof.
- the hot source motor is arranged so that the volume of the high temperature working chamber is larger than the volume of the low temperature working chamber.
- the stroke of the high temperature piston can be increased relative to that of the low temperature piston.
- the bore of the high temperature cylinder can be increased relative to that of the low temperature cylinder.
- This feature has the advantage of further expanding the working gas in the high temperature working chamber to recover more engine work.
- the working gas can be expanded to a gas pressure as close as possible to atmospheric pressure in order to limit the residual loss at the exhaust.
- the pressure prevailing in the high temperature working chamber at the end of the expansion phase is between 1 bar and 1.5 bar, preferably between 1.2 bar and 1.3 bar.
- the nominal pressure prevailing in the exchanger is then between 4 and 5 bars absolute and the heat transfer fluid can have a temperature between 500 and 900 ° C for example.
- the motor is arranged so that, at the end opposite the mouths, the internal passages open out through the side wall of the plug by orifices which selectively communicate with fixed connections depending on the position. angular of the bushel.
- the plug ports allow working gas to flow from the internal passages of the plug to the fittings or from fittings to the internal passages of the plug.
- the geometry of the at least one plug is such that the orifice is capable of communicating with the corresponding connector 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 comprise a cold fitting communicating with the cold end of the exchanger and a hot fitting communicating with the end. heat exchanger.
- Said fittings include an inlet fitting communicating with the inlet of the working gas and an exhaust fitting communicating with the outlet of the working gas.
- the motor comprises two fixed connections, a so-called “high pressure” connection and a so-called “low pressure” connection.
- 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 consists of an inlet fitting and an exhaust fitting.
- the at least one internal passage is arranged in a rectilinear manner in the at least one rotary valve; this characteristic makes it possible in particular to limit the pressure losses during the flow of gas in the at least one rotary valve,
- the at least one internal passage is arranged so that the at least one mouth and the at least one orifice are diametrically opposed
- the at least one mouth is offset axially with respect to the at least one orifice
- the at least one mouth is aligned circumferentially with respect to the at least one orifice
- the at least one internal passage extends in a direction perpendicular, or radial, to the axis of rotation of the at least one rotary valve
- the distribution is arranged and configured so that the at least one valve has, in operation, a speed of rotation equal to the speed of rotation of the crankshaft, in particular when the at least one mouthpiece is offset axially with respect to the 'at least one orifice,
- the distribution is arranged and configured so that the at least one valve has, in operation, a speed of rotation equal to half the speed of rotation of the crankshaft, in particular when the at least one mouthpiece is aligned circumferentially by in relation to at least one orifice,
- - at least one mouthpiece comprises two mouthpieces for the same internal passage, capable of communicating simultaneously with the working chamber, by two lights, - the at least one internal passage comprises two internal passages leading in parallel to the same resource, each capable of communicating simultaneously with a lumen of the cylinder head,
- the mouths and orifices or openings of the plug are only arranged through the peripheral or circumferential wall of the plug
- each mouthpiece can coincide with a lumen; 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 valve.
- the gas passes through the two openings of the high pressure valve by passing through the two ports of the cylinder head so that the flow is split in half to pass through the two lumens and the two mouths, forming two parallel flow lines via two internal passages. After the mouth, each flow line circulates in a duct formed by the internal passage to open out through an orifice.
- the openings, the openings and the orifices have a rectangular shape in order to limit the pressure drops.
- internal passages have a rectangular cross section.
- the at least one rotary valve comprises a low pressure valve controlling the selective communication of the working chambers with the intake and the exhaust.
- the at least one rotary valve comprises a high pressure valve controlling the selective communication of the working chambers with the hot and cold ends of the exchanger.
- This embodiment also satisfies the concern to provide a relatively large passage section for the gas going to and returning from the exchanger, since the gas then being compressed, the volume which must flow is smaller than at the inlet and to the exhaust.
- a high pressure plug with a diameter greater than the diameter of the low pressure plug makes it possible to further enlarge the passage section of the internal passages, going to the exchanger and back.
- the engine distribution is arranged and configured so that the high pressure valve has a rotational speed equal to the rotational speed of the crankshaft.
- This feature has the advantage of making working gas passages (openings) of short duration with large sections.
- the engine distribution is arranged and configured so that the low pressure valve has a rotational speed equal to half the rotational speed of the crankshaft.
- the at least one rotary plug comprises four plugs:
- This characteristic has the advantage of dissociating both the so-called “high pressure” flows and the so-called “low pressure” flows on the one hand, and the so-called “high temperature” flows and the so-called “low temperature” flows on the other hand. .
- the at least one rotary plug comprises a peripheral groove delimiting a part of the plug above the low temperature cylinder and a part of the plug above the high cylinder. temperature, said groove being arranged to receive a sealing device for closing the gap between the peripheral wall of the plug and an adjacent surface of the cylinder head on the one hand and an adjacent surface of a connector on the other hand.
- the at least one plug comprises two coaxial parts:
- a working gas guiding part comprising internal passages opening out radially through at least one mouth which communicates selectively with a working chamber via at least one slot made in the cylinder head, and
- a working gas distribution part arranged at the periphery of the guide part and movable relative to the guide part, the distribution part comprising at least one window which selectively communicates the working chamber with at least one of said internal passages so that working gas selectively flows between the working chamber and the various resources.
- each lumen of the cylinder head may be surrounded by a sealing device to close the gap between the peripheral wall of the plug and an adjacent surface of the cylinder head.
- an engine assembly comprising an external hot source engine according to one or more of the preceding characteristics and a heat exchanger having a caloreceptor path extending between a cold end and a heat exchanger. hot end selectively connected to the low temperature working chamber and the high temperature working chamber towards the end of a compression phase and towards the start of an expansion phase, respectively.
- the heat exchanger is of the counter-current type
- the heat exchanger comprises a heat transfer path traversed by the exhaust gases of an internal combustion engine
- the heat exchanger comprises a heat transfer path traversed by a gas flow having a temperature between 300 ° C and 900 ° C, preferably between 500 ° C and 900 ° C (degrees Celsius).
- FIG.l is a schematic representation of a split-cycle external hot source engine according to one embodiment, wherein said engine comprises two plugs illustrated according to a first embodiment, a low pressure plug and a high pressure plug each surmounting two cylinders, the engine comprising two cylinders: a low temperature cylinder, to the left of the figure, and a high temperature cylinder to the right of the figure, the position of the pistons being represented randomly, the engine being coupled with a heat exchanger, the engine and exchanger assembly being seen in section;
- Figure 2 is a perspective view and partial longitudinal section of an external heat source engine with divided cycle according to one embodiment, the section plane passing through the axes of the two pistons but without passing through the cylinder head, the engine comprising two cylinders: a low temperature cylinder, to the right of the figure, and a high temperature cylinder to the left of the figure;
- Figure 3 is an exploded perspective view of a high pressure part of an engine according to one embodiment, Figure 3 showing in perspective a high pressure valve according to one embodiment, the high pressure valve being placed between the cylinder head and a fitting provided to cover the high pressure valve, and comprising a low temperature part and a high temperature part;
- Figure 4 is an exploded perspective view of a high pressure part of an engine according to Figure 3, Figure 4 showing in perspective a low pressure valve according to one embodiment, the low pressure valve being placed between the cylinder head and a fitting provided to cover the low pressure valve, and comprising a low temperature part and a high temperature part;
- Figure 5 is a cross-sectional view of an engine according to Figures 2 to 4, the sectional plane passing through the axis of the low temperature cylinder, said engine comprising a low pressure valve and a high valve pressure, Figure 5 illustrating, at a time Tl in the chamber low temperature working, a phase of admission of the working gas via the low pressure valve into the low temperature working chamber, and showing the position of the various moving parts including the angular position of the valves;
- FIG. 6 is a cross-sectional view of an engine according to Figures 2 to 4, the sectional plane passing through the axis of the high temperature cylinder, said engine comprising a low pressure valve and a high valve pressure, FIG. 6 illustrating, at the same instant Tl in the high temperature working chamber, a phase of expansion or expansion of the working gas coming from the hot end of the exchanger via the high pressure valve and moving into the chamber high temperature working, and showing the position of the various moving parts including the angular position of the plugs;
- Figure 7 is a cross-sectional view of an engine according to Figure 5, Figure 7 illustrating, at a time T2 in the low temperature working chamber, a phase of the start of compression of the gas. work present in the low temperature working chamber, the low temperature piston being positioned at bottom dead center;
- Figure 8 is a cross-sectional view of an engine according to Figure 6, Figure 8 illustrating, at the same time T2 in the high temperature working chamber, an end of expansion and start phase exhausting the relaxed working gas into the high temperature working chamber, the high temperature piston being positioned at the bottom dead center;
- Figure 9 is a cross-sectional view of an engine according to Figures 5 and 7, Figure 7 illustrating, at a time T3 in the low temperature working chamber, a phase of transfer of the working gas compressed from the low temperature working chamber to the cold end of the exchanger;
- Figure 10 is a cross-sectional view of an engine according to Figures 6 and 8, Figure 10 illustrating, at the same time T3 in the high temperature working chamber, an exhaust gas phase of relaxed working in the high temperature working chamber;
- Figure 11 is a cross-sectional view of an engine according to Figures 5, 7 and 9, Figure 11 illustrating, at a time T4 in the low temperature working chamber, a start phase of gas admission work via the low pressure valve in the low temperature working chamber, the low temperature piston being positioned at top dead center;
- Figure 12 is a cross-sectional view of a motor according to Figures 6, 8 and 10, Figure 12 illustrating, at the same time T4 in the high temperature working chamber, a transfer start phase heated working gas coming from the hot end of the exchanger via the high pressure valve in the high temperature working chamber to be expanded, the high temperature piston being positioned at top dead center;
- FIG. 13 is an exploded perspective view of a plug according to a second embodiment, the plug comprising two coaxial parts, a distribution part and a guide part, the guide part comprising two mouths, the distribution part comprising two windows, the distribution part being provided to cover the guide part of the plug.
- 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 characteristics), if this selection of characteristics 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 preferably functional characteristic without structural details, and / or with only part of the structural details if this part alone is sufficient to confer a technical advantage or to differentiate the invention from the state of the art. earlier.
- FIG. 1 schematically illustrates an assembly comprising a split-cycle external hot source engine 1 and a heat exchanger 6.
- the engine comprises: - an engine block in which is formed two cylindrical cavities called cylinder: a low temperature cylinder 2 and a high temperature cylinder 8 (shown by Figure 1 separately for the understanding of the invention), forming a pair of cylinders allowing to perform a divided thermodynamic cycle in said pair of cylinders; the cylinders 2 and 8 being arranged longitudinally in a single engine block, see figure 2,
- a low temperature piston 3 moving back and forth in the low temperature cylinder 2
- a high temperature piston 9 moving back and forth in the high temperature cylinder 8
- cylinder head 4 covering the engine block above the low temperature 2 and high temperature 8 cylinders, so that the cylinder head 4 defines on the one hand with the low temperature piston 3 and the low temperature cylinder 2 a low working chamber temperature 52 for a working gas, typically air, and on the other hand with the high temperature piston 9 and the high temperature cylinder 8 a high temperature working chamber 58 for the working gas,
- a working gas typically air
- the low temperature working chamber 52 with the following resources: an inlet A of working gas then a cold end B of the heat exchanger 6, the high temperature working chamber 58 with the following resources: a hot end C of the heat exchanger 6, then an exhaust D.
- the engine is connected to a heat exchanger 6 for heat exchange between the working gas, called the heat-receiving fluid, and a heat transfer fluid.
- the heat exchanger 6 is of the countercurrent type. Referring to Figure 1, it comprises a heat transfer path 61, represented by a zigzag conduit, traversed by the heat transfer fluid from right to left. It further comprises a heat receiver path 62, also represented by a zigzag duct, under the heat transfer path 61, so that the working gas travels the heat receiver path from left to right.
- the calo- route ceding is distinct from the heat-receptor 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. Likewise, one or more fittings or pipes are connected to the engine to provide the intake and the exhaust.
- the distribution comprises two rotary plugs 20, 30. They are mounted in rotation in the cylinder head 4, above the working chambers 52 and 58.
- the axes of rotation of the two plugs are parallel to each other, and orthogonal to the axis of cylinders 2 and 8.
- the plugs comprise a so-called "low pressure" plug 30 arranged and configured to control the selective communication of the lower working chamber temperature 52 with the inlet A and control the selective communication of the high temperature working chamber 58 with the exhaust D.
- the plugs include a so-called "high pressure" plug 20 arranged and configured to control the selective communication of the working chamber low temperature 52 with the cold end B of the heat exchanger 6 and control the selective communication of the high temperature working chamber 58 with the hot end C of the heat exchanger 6.
- the high pressure plug 20 is used only to control the flow of working gas between the working chambers and the heat exchanger.
- the low pressure valve is only used to control the intake and exhaust. This characteristic makes it possible to simplify the construction of the engine by separating the so-called “high pressure” flows and the so-called “low pressure” flows and to reduce its bulk.
- 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 peripheral wall of the valve 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 motion 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 made in the cylinder head and at least one lumen formed in a fixed connector 60, 70.
- the opening opposite the lumen of the cylinder head is called the mouthpiece. working gas between a working chamber and a bushel or vice versa.
- the orifice is called the opening opposite a connector when the working gas passes between a plug and a connector or vice versa.
- the low pressure valve comprises:
- two internal passages comprising two inlet openings 32 and two inlet openings 34, said passages being arranged in a rectilinear manner and in a perpendicular direction at the axis of said plug,
- two internal passages comprising two exhaust openings 31 and two exhaust ports 33, said passages being arranged in a rectilinear manner and in a direction perpendicular to the 'axis of said plug, and the high pressure plug comprises:
- two internal passages comprising two cold openings 21 and two cold openings 23, said passages being arranged in a rectilinear manner and according to a direction diagonal to the axis of said plug, said direction forming a non-zero angle with respect to the axis of said plug or a non-zero angle with respect to the radial direction of said plug, so that the orifices are offset axially by relative to the mouths along the wall of said plug, and
- a high engine comprising a cylinder head 4 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" assembly, in accordance with FIG. 2.
- the top motor comprises the high pressure valve 20 which is designed to be covered by a fixed connection called “high pressure” 60.
- the upper motor comprises the valve low pressure 30 which is designed to be covered by a fixed so-called “low pressure” connection 70.
- the cylinder head 4 has a receiving surface 40hp in order to receive the high pressure valve, and a receiving surface 40bp in order to receive the low pressure valve.
- Each 40hp, 40bp receiving surface has a concave shape, so as to cooperate by formally complementary with each of the bushels.
- the receiving surface has a section in the form of an arc of a circle that is 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 receiving surfaces 40hp, 40bp.
- the high pressure plug like the low pressure plug has, according to a cross section, a circular outer shape.
- the two bushels have a substantially identical diameter.
- the 40hp receiving surface comprises four high pressure ports: two pairs of adjacent ports 41H0, 41H3, each pair being provided to cooperate with a cylinder.
- the 41H0 lights cooperate with the low temperature cylinder, and the 41H3 lights cooperate with the high temperature cylinder.
- the reception surface 40bp comprises four low pressure ports: two pairs of adjacent ports 41adm, 41ech, each pair being provided to cooperate with a cylinder.
- the 41adm lights cooperate with the low temperature cylinder, and the 41ech lights cooperate with the high temperature cylinder.
- the slots have a rectangular shape to limit the pressure drops during the circulation of the flow of working gas.
- the two cold mouths 21 are intended to coincide with the two openings 41H0 of the cylinder head so that the working gas can flow from the low temperature working chamber to the high pressure valve 20.
- the cold mouths 21 are arranged with adjacent manner and are axially aligned with the periphery of the high pressure valve along a direction parallel to the axis of rotation of said valve.
- the cold mouthpieces of identical dimensions, have a substantially rectangular shape, the longitudinal dimension of which extends in a direction which is parallel to the axis of rotation of the plug.
- the cold orifices 23 are arranged on the periphery of the high pressure valve.
- the cold orifices 23 are intended to coincide respectively with openings 63 of the high pressure connector 60.
- the cold orifices 23 have a rectangular shape, the longitudinal dimension of which extends in a direction which is orthogonal, or circumferential, to the axis of rotation. of the bushel.
- the two hot mouths 22 are intended to coincide with the two ports 41H3 of the cylinder head so that the working gas can flow from the high pressure valve 20 to the high temperature working chamber.
- the hot mouths 22 are arranged adjacent and are axially aligned with the periphery of the high pressure plug along a direction parallel to the axis of rotation of said plug.
- the hot mouths of identical dimensions, have a substantially rectangular shape, the longitudinal dimension of which extends in a direction which is parallel to the axis of rotation of the plug.
- the hot orifices are arranged on the periphery of the high pressure valve.
- the hot ports are intended to coincide respectively with openings 65 of the high pressure connector 60.
- the hot ports have a rectangular shape, the longitudinal dimension of which extends in a direction which is orthogonal, or circumferential, to the axis of rotation of the plug. .
- the high pressure connector 60 has a covering surface 69 arranged and configured to cooperate by formally complementary with the peripheral surface of the high pressure valve.
- the covering surface 69 has, in cross section, a shape substantially of an arc of a circle.
- each hot mouthpiece has, along the circumference of the plug, an angular opening of between 20 and 50 degrees, preferably between 25 and 35 degrees. Since the engine carries out four main phases and 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 drops and bulk (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.
- each light 41hp has, along the circumference of the receiving surface 40, an angular opening of, for example, between 15 and 30 degrees.
- the orifices have, along the circumference of the plug, an angular opening of between 100 and 350 degrees, preferably between 120 and 150 degrees.
- the two inlet openings 32 are intended to coincide with the two ports 41 adm of the cylinder head so that the working gas can flow from the low pressure valve 30 to the low temperature working chamber.
- the inlet mouths 32 are arranged adjacent and are axially aligned with the periphery of the low pressure plug, along a direction parallel to the axis of rotation of the plug.
- the inlet openings 32 of identical dimensions, have a substantially rectangular shape, the longitudinal dimension of which extends in a direction which is parallel to the axis of rotation of the valve.
- the two inlet ports 34 arranged at the periphery of the low pressure valve.
- the inlet ports 34 are intended to coincide respectively with openings 73 of the low pressure connection 70.
- the inlet ports 34 have a rectangular shape, the longitudinal dimension of which extends in a direction which is parallel to the axis of rotation. of the bushel.
- the two exhaust openings 31 are intended to coincide with the two openings 41ech of the cylinder head 4 so that the working gas can flow from the high temperature working chamber to the low pressure valve 30.
- the two openings d The exhaust 31 are arranged adjacent and are axially aligned with the periphery of the low pressure valve, along a direction parallel to the axis of rotation of the valve.
- the exhaust openings of identical dimensions, have a substantially rectangular shape, the longitudinal dimension of which extends in a direction which is parallel to the axis of rotation of the plug.
- the exhaust ports 33 are arranged on the periphery of the low pressure valve.
- the exhaust ports 33 are intended to coincide respectively with openings 75 of the low pressure connection 70.
- the exhaust ports 33 have a rectangular shape, the longitudinal dimension of which extends in a direction which is parallel to the axis of rotation. of the bushel.
- the low pressure connection 70 has a covering surface 79 arranged and configured to cooperate by formally complementary with the peripheral surface of the low pressure valve.
- the covering surface 79 has, in cross section, a shape substantially of an arc of a circle.
- the high pressure valve comprises a groove 25 arranged on the peripheral surface of said valve, between the low temperature part and the high temperature part, see FIG. 3.
- the low pressure valve comprises a groove 35 arranged on the peripheral surface of said plug, between the low temperature part and the high temperature part, see FIG. 4.
- the groove 25, 35 makes it possible to receive a sealing device in order to close the gap between the peripheral wall of the plug and a surface of reception on the one hand, and a covering surface of a fitting on the other hand.
- a plug 10 made of two coaxial parts comprising a so-called “guide” part 11 and a so-called “distribution” part 16.
- the guide part 11 has a generally cylindrical shape and is fixed relative to the cylinder head of the engine.
- the guide part is made in a similar way to the plugs described above.
- the guide part shown in Figure 13 is arranged to cooperate with a single working chamber.
- the guide part has two mouths 21.
- the distribution part 16 has a generally tubular shape which surrounds the guide part 11 and which is rotatable relative to the guide part.
- the distribution part 16 of the valve is rotatably mounted in the cylinder head of the engine.
- the distribution part comprises at least one window which selectively communicates the working chamber with at least one of said internal passages so that the working gas flows selectively between the working chamber and the different resources and vice versa.
- the distribution part comprises two windows called mouth windows, for the transfer of the working gas from the working chamber to the cold end of the exchanger.
- the rotary movement of the distribution part relative to the guide part 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 working gas between the valve. working chamber and exchanger. Every window coincides selectively with at least one lumen of the breech and at least one mouthpiece.
- at least one window called the orifice window, may coincide with at least one orifice and at least one lumen of a connector.
- the two-part coaxial plug has the advantages of simultaneously limiting thermal losses and pressure drops, thus making it possible to improve the efficiency and / or the performance of a split-cycle external hot-source engine.
- FIGS. 5 and 6 represent the operation of the motor during a first instant Tl.
- FIGS. 7 and 9 represent the operation of the motor during a second instant T2, which follows on from the instant Tl.
- FIGS. 9 and 10 represent the operation of the engine during a third instant T3, which is consecutive to the instant T2.
- FIGS. 11 and 12 represent the operation of the motor during a fourth instant T4, which follows on from instant T3.
- Figures 5, 7, 9 and 11 show the operation of the engine on the low temperature cylinder side
- Figures 6, 8, 10 and 12 show the operation of the engine on the high temperature cylinder side.
- a mouthpiece, an orifice and a lumen will be described for each figure.
- the high pressure 20 and low pressure 30 plugs pivot angularly counterclockwise.
- a phase of admission of a working gas into the low temperature working chamber 52 a phase of admission of a working gas into the low temperature working chamber 52.
- the synchronization of the piston 3 and the plugs 20, 30 is such that the movement of the piston 3 is downward while the rotation of the low pressure plug 30 allows an inlet mouth 32 of the low pressure plug 30 to communicate with a lumen 41 adm of the cylinder head 4 and simultaneously allows an inlet port 34 to communicate with a lumen (not visible) of a low pressure fitting 70.
- the working gas passes through the internal passage between the inlet port 34 and the inlet mouth 32 so as to be admitted into the low temperature working chamber 52, see arrow fA.
- no cold mouth 21 of the high pressure valve communicates with a lumen of the cylinder head.
- the working gas is preferably air taken from the outside environment.
- the working gas heated by the heat exchanger and leaving the high pressure plug 20 expands in the high temperature working chamber 58.
- the synchronization of the piston 9 and the plugs 20 , 30 is such that the movement of the piston 9 is downward while the rotation of the high pressure plug 20 allows the hot mouth 22 of the high pressure plug to communicate with a lumen 41H3 of the cylinder head 4, and simultaneously allows a hot orifice communicate with a light (not visible) of a high pressure connection connected to the hot end of the heat exchanger.
- the working gas passes through the internal passage between the hot port and the hot mouth 22 so as to be transferred from the heat exchanger to the high temperature working chamber to be relaxed.
- no exhaust port of the low pressure valve communicates with a lumen of the cylinder head.
- the two pistons 3 and 9 are located respectively at 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 port 41 adm of the cylinder head 4.
- no cold mouth 21 of the high pressure valve 20 does not communicate with a light in the cylinder head.
- the synchronization of the piston 3 and the plugs 20, 30 is such that the piston 3 will rise so that the working gas trapped in the low temperature working chamber 52 will be compressed therein.
- the hot mouth 22 of the high pressure valve no longer communicates, even partially, with an opening in the cylinder head.
- the synchronization of the piston 9 and the plugs 20, 30 is such that the rotational movement of the low pressure plug 30 allows the exhaust port 31 to be angularly offset by a few degrees with respect to a lumen 41ech of the cylinder head 4, and simultaneously allows an exhaust port to start communicating with a lumen 75 of a low pressure fitting 70, so that an exhaust phase will begin.
- a phase of end compression of the working gas and a phase of transfer of the compressed working gas from the low temperature working chamber 52 to the heat exchanger there is illustrated a phase of end compression of the working gas and a phase of transfer of the compressed working gas from the low temperature working chamber 52 to the heat exchanger.
- the synchronization of the piston 3 and the plugs 20, 30 is such that the movement of the piston 3 is upward while the rotation of the high pressure plug 20 allows a cold mouth 21 of the high pressure plug 20 to communicate with a light 41H0 of the cylinder head 4.
- Simultaneously synchronization allows a cold port (not visible) to communicate with a light (not visible) from a fitting on the cold end of the heat exchanger.
- the working gas passes through the internal passage between the cold mouth 21 and the cold orifice so as to be transferred to the heat exchanger to be heated.
- the two low temperature 3 and high temperature 9 pistons are located respectively at top dead center.
- the high pressure valve 20 has rotated so that the cold mouth 21 of the high pressure valve 20 no longer communicates, even partially, with a port 41H0 of the cylinder head 4.
- the synchronization of the piston 3 and the plugs 20, 30 is such that the rotational movement of the low pressure plug 30 allows the inlet port 32, which was, one revolution of the crankshaft previously, an inlet port 34, to be angularly offset by a few degrees with respect to a lumen 41adm in the cylinder head 4.
- the synchronization allows an intake port 34 which was, one revolution of the crankshaft previously, an intake port 32, to begin communicating with a lumen (not visible) of a low pressure connection 70, so that an intake phase, as shown in FIG. 7, will begin.
- the synchronization of the plug 3 and the plugs 20, 30 is such that the rotational movement of the high pressure plug 20 allows the hot mouth 22 to be angularly offset by a few degrees to a light 41H3 of the cylinder head 4.
- the synchronization allows a hot (not visible) port to start communicating with a light (not visible) of a high pressure fitting 60, so that a phase of transfer of heated working gas will begin from the heat exchanger to the high temperature working chamber to be expanded, as shown in Figure 9.
- the low pressure valve 30 From the low pressure side, the low pressure valve 30 has rotated so that the mouthpiece exhaust 31 of the low pressure valve no longer communicates, even partially, with a port 41ech of the cylinder head 4.
- the low temperature 2 and high temperature 8 pistons are respectively connected via a connecting rod to the same crankshaft.
- the arrangement of the pistons 2 and 8, of the connecting rods and of the crankshaft is arranged so that the rise and fall of the pistons take place synchronously.
- the speed of rotation of the low pressure valve 30 is equal to half the speed of rotation of the crankshaft.
- This last characteristic has the advantage of limiting friction.
- an intake mouth 32 becomes an intake port 34 and intake port 34 becomes an intake port 32, see Figure 5 illustrating an intake phase and Figure 11 illustrating a moment of pre-admission.
- an exhaust port 31 becomes an exhaust port 33 and an exhaust port 33 becomes an exhaust port 31.
- the speed of rotation of the high pressure valve 20 is equal to the speed of rotation of the crankshaft.
- This last characteristic has the advantage of offering large opening sections for a very short time.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1915086A FR3105302B1 (fr) | 2019-12-20 | 2019-12-20 | Moteur à source chaude externe à cycle divisé à boisseaux |
PCT/EP2020/087287 WO2021123358A1 (fr) | 2019-12-20 | 2020-12-18 | Moteur a source chaude externe a cycle divise a boisseaux |
Publications (1)
Publication Number | Publication Date |
---|---|
EP4077902A1 true EP4077902A1 (fr) | 2022-10-26 |
Family
ID=69811305
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20838061.8A Pending EP4077902A1 (fr) | 2019-12-20 | 2020-12-18 | Moteur a source chaude externe a cycle divise a boisseaux |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP4077902A1 (fr) |
FR (1) | FR3105302B1 (fr) |
WO (1) | WO2021123358A1 (fr) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3555814A (en) * | 1968-11-26 | 1971-01-19 | Arthur L Morsell | Internal combustion engines |
JP2005325711A (ja) * | 2004-05-12 | 2005-11-24 | Toyota Motor Corp | 熱エネルギ回収装置 |
CN101365868B (zh) * | 2005-03-09 | 2015-03-04 | 扎杰克优质发动机股份有限公司 | 内燃机及改进燃烧室的方法 |
FR2905728B1 (fr) | 2006-09-11 | 2012-11-16 | Frederic Thevenod | Moteur hybride a recuperation de la chaleur d'echappement |
FR2954799B1 (fr) | 2009-12-28 | 2012-10-19 | Frederic Olivier Thevenod | Machine thermique a source chaude externe, groupe de production d'energie et vehicule associes. |
FR3069884B1 (fr) | 2017-08-02 | 2020-02-21 | H2P Systems | Moteur a source chaude externe a boisseaux |
-
2019
- 2019-12-20 FR FR1915086A patent/FR3105302B1/fr active Active
-
2020
- 2020-12-18 EP EP20838061.8A patent/EP4077902A1/fr active Pending
- 2020-12-18 WO PCT/EP2020/087287 patent/WO2021123358A1/fr unknown
Also Published As
Publication number | Publication date |
---|---|
WO2021123358A1 (fr) | 2021-06-24 |
FR3105302A1 (fr) | 2021-06-25 |
FR3105302B1 (fr) | 2021-12-24 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2064431B1 (fr) | Moteur thermique à source chaude externe | |
WO2019025555A1 (fr) | Moteur a source chaude externe a boisseaux | |
FR2994250A1 (fr) | Chambre de combustion cvc pour turbomachine d'aeronef comprenant une valve d'admission / d'echappement a tournant spherique | |
EP4077902A1 (fr) | Moteur a source chaude externe a cycle divise a boisseaux | |
FR2904057A1 (fr) | Circuit d'alimentation d'un moteur thermique avec mise en rotation des gaz et moteur thermique correspondant | |
EP0625631B1 (fr) | Boisseau rotatif amélioré | |
EP4077891A1 (fr) | Boisseau en deux parties coaxiales, et moteur a source chaude externe comprenant celui-ci | |
EP3259449B1 (fr) | Machine de compression et detente de type ciseaux utilisee dans un systeme de recuperation d'energie thermique | |
AU2006223794A1 (en) | Rotary engine | |
FR2654464A1 (fr) | Systeme de fermeture et d'ouverture rapides de la section d'ecoulement de fluide d'un conduit, et moteur thermique a deux temps incorporant ledit systeme. | |
EP0358655A1 (fr) | Procede et dispositif d'amenagement d'un moteur a deux temps a post-remplissage. | |
WO2006016019A1 (fr) | Moteur a piston rotatif tripode 6 temps | |
FR2634821A1 (fr) | Perfectionnement aux moteurs a capsulisme | |
FR2941740A1 (fr) | Moteur rotatif a rotor circulaire | |
FR2957631A1 (fr) | Element de moteur a combustion interne a detente prolongee et moteur a combustion interne comprenant un ou plusieurs de ces elements | |
WO2021084176A1 (fr) | Moteur à combustion interne | |
FR3033000B1 (fr) | Machine de compression et detente d'un fluide, ainsi que son utilisation dans un systeme de recuperation d'energie thermique | |
FR2883036A1 (fr) | Moteur thermique, rotatif a rotor unique et deux pistons cylindriques, biconvexes et a mouvements alternatifs | |
FR2819853A1 (fr) | Mecanisme bielles-manivelles rotatif | |
FR2805566A1 (fr) | Moteur a combustion interne | |
BE349289A (fr) | ||
FR2803874A1 (fr) | Moteur alternatif a combustion interne a chemise deplacable munie d'un orifice de distribution | |
WO2007118940A1 (fr) | Moteur rotatif a rotor unique et 2 pistons cylindriques alternatifs | |
WO2001073266A1 (fr) | Machine motrice et receptrice a mouvement rotatif | |
FR2835570A1 (fr) | Plaque motrice multicellulaire parallelepipedique, entierement hermetique |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: UNKNOWN |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE |
|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20220708 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAV | Request for validation of the european patent (deleted) | ||
DAX | Request for extension of the european patent (deleted) | ||
19U | Interruption of proceedings before grant |
Effective date: 20230531 |
|
19W | Proceedings resumed before grant after interruption of proceedings |
Effective date: 20240502 |