EP3585993B1 - Regeneratives kühlsystem - Google Patents

Regeneratives kühlsystem Download PDF

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Publication number
EP3585993B1
EP3585993B1 EP18707106.3A EP18707106A EP3585993B1 EP 3585993 B1 EP3585993 B1 EP 3585993B1 EP 18707106 A EP18707106 A EP 18707106A EP 3585993 B1 EP3585993 B1 EP 3585993B1
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Prior art keywords
duct
gas
regeneration
cooling system
outlet
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EP18707106.3A
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French (fr)
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EP3585993A1 (de
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Vianney Rabhi
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    • 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
    • F02G1/00—Hot gas positive-displacement engine plants
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/055—Heaters or coolers
    • 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
    • F02G1/04—Hot gas positive-displacement engine plants of closed-cycle type
    • F02G1/043—Hot gas positive-displacement engine plants of closed-cycle type the engine being operated by expansion and contraction of a mass of working gas which is heated and cooled in one of a plurality of constantly communicating expansible chambers, e.g. Stirling cycle type engines
    • F02G1/053—Component parts or details
    • F02G1/057—Regenerators

Definitions

  • the present invention relates to a regenerative cooling system which constitutes, among other things, an improvement of the heat engine with transfer-expansion and regeneration which was the subject of patent application No. FR 15 51593 of February 25, 2015 owned by the applicant and the patent published on 1 September 2016 under No. US 2016/0252048 A1 which also belongs to the applicant.
  • said cycle leads to engines which deliver an efficiency which is substantially higher than that of spark ignition engines. Said efficiency is comparable to that of fast diesel engines. However, it is still lower than that of slow, very large displacement two-stroke diesel engines found, for example, in naval propulsion or stationary electricity production.
  • the thermal engine with transfer-expansion and regeneration which is the subject of patent application No. FR 15 51593 and documents FR3032235 and WO2016120560 has been designed to remedy these shortcomings.
  • Said engine has the particularity of using the regenerated Brayton cycle no longer by means of centrifugal compressors and turbines, but by means of positive displacement machines or at least by means of a positive pressure regulator formed around a "cylinder". regulator ".
  • each end of said expansion cylinder is closed by an expansion cylinder head.
  • said cylinder accommodates a double-acting expansion piston to form two transfer-expansion chambers of variable volume.
  • Said piston can move in the expansion cylinder to transmit work to a power output shaft via a connecting rod and a crankshaft known per se.
  • the volumetric regulator is effectively made up of a cylinder, which is not taught by the state of the art, which reports related machines.
  • the patent US 2003/228237 A1 of December 11, 2003 includes a compressor, a regeneration heat exchanger, a heat source and an expander, however, the latter is not a cylinder but what the inventors authors of said patent have called a "gerotor".
  • the second condition is that the inlet and outlet of the gases in the pressure reducing cylinder are regulated by duly phased intake and exhaust metering valves, which leads to the "pressure / volume" diagram to which a figure in the figure is devoted.
  • the third condition is that the sealing device between the piston and the cylinder can operate at very high temperature.
  • This new sealing device and without direct contact with the expansion cylinder makes it possible to operate said cylinder at high temperature, while the intake and exhaust metering valves included in the cylinder heads which close said cylinder make it possible to maximize the efficiency of the cylinder. thermal engine with transfer-expansion and regeneration.
  • the internal walls of the expansion cylinder must be brought to high temperature so that the hot gases introduced into said cylinder do not cool on contact with said cylinder. walls, or at least, are cooled as little as possible by said walls. This applies at least to the internal walls of the expansion cylinder proper, and to those of the cylinder heads with which said cylinder cooperates.
  • the patent application FR 15 51593 provides that the expansion cylinder, the cylinder heads of the expansion cylinder and the expansion piston of the transfer-expansion and regeneration heat engine can be made of materials resistant to very high temperatures such as ceramics based on alumina, zirconia or carbide silicon.
  • the temperature of said gases therefore directly determines the temperature to which the materials constituting the hot parts of the expansion cylinder of the transfer-expansion and regeneration heat engine must withstand.
  • the temperature resistance of said materials determines the maximum efficiency accessible by said motor.
  • Said materials are mainly ceramics such as alumina, zirconia, silicon carbide or silicon nitride. These materials are hard and difficult to machine. Consequently, the cost price of the finished parts is relatively high, which is a brake on the adoption by the automotive industry of the transfer-expansion and regeneration heat engine which is the subject of the patent application.
  • FR 15 51593 FR 15 51593 .
  • said industry is aimed at the mass market, it is highly sensitive to the manufacturing cost price, which must remain as low as possible.
  • FR 15 51593 belonging to the applicant.
  • said system can also be applied without restriction to the regulator of any other regenerating Brayton cycle engine, whether said regulator is of the centrifugal, positive-displacement or some other type, and provided that it cooperates with a regenerator of some kind. type whatever.
  • the regenerative cooling system comprises an enclosure inlet port which is connected to the outlet of the gas regulator by an enclosure inlet duct, the effective section of which is regulated by a flow rate regulating valve. .
  • the regenerative cooling system comprises an enclosure outlet port which is connected to the regeneration low-pressure duct by an enclosure outlet duct, the effective section of which is regulated by a flow control valve.
  • the regenerative cooling system comprises an outlet of the gas regulator which is connected to the low-pressure regeneration duct by an enclosure bypass duct.
  • the regenerative cooling system according to the present invention comprises an effective section of the enclosure bypass duct which is regulated by a flow control valve.
  • the regenerative cooling system according to the present invention comprises an exterior of the cooling enclosure which is coated with a heat shield.
  • Figure 1 is a schematic representation in side view of the regenerative cooling system according to the invention as it can be implemented on the heat engine with transfer-expansion and regeneration object of patent application No. FR 15 51593 belonging to the applicant, and according to a variant of said system according to which the outlet of the gas regulator is connected to the low-pressure regeneration duct by an enclosure bypass duct, while the effective section of said bypass duct and of the outlet duct chamber is regulated by a flow control valve.
  • the regenerative cooling system 100 is provided for a regenerative heat engine 1, the latter comprising at least one regeneration heat exchanger 5 which has a high-pressure regeneration duct 6 in which circulates in order to be preheated therein a working gas 81 which has been previously compressed by a compressor 2.
  • said gas 81 is superheated by a heat source 12 before being introduced into a gas regulator 78 in which it is expanded to produce work on a power output shaft 17. .
  • the working gas 81 is then expelled at the outlet of the gas regulator 78 and then introduced into a low-pressure regeneration duct 7 which the regeneration heat exchanger 5 has, said gas 81 - by circulating in said duct 7 - yielding a large part of its residual heat to the working gas 81 circulating in the high-pressure regeneration duct 6.
  • the regenerative cooling system 100 comprises at least one cooling enclosure 79 which surrounds all or part of the gas pressure reducer 78 and / or the heat source 12 and / or a hot gas inlet duct 19 which connects said source 12 to said regulator 78, while a space for the circulation of gases 80 is left between said enclosure 79 on the one hand, and / or said regulator 78 and / or said source 12 and / or said duct 19 of on the other hand, the working gas 81 being able to circulate in said space 80.
  • cooling enclosure 79 can be made of stamped or hydro-formed stainless steel sheet, and possibly be made in several parts assembled together by welding, screwing, or riveting, said enclosure then being able to be fixed directly or indirectly on the components 78, 12, 19 that it envelops.
  • the figure 1 illustrates that the regenerative cooling system 100 according to the invention further comprises at least one enclosure inlet port 82 which is directly or indirectly connected to the outlet of the gas regulator 78 and through which all or part of the working gas 81 expelled from said regulator 78 via said outlet can enter the gas circulation space 80.
  • the regenerative cooling system 100 also comprises at least one enclosure outlet port 83 which is directly or indirectly connected to the low-pressure regeneration duct 7 and via which the working gas 81 can exit from the gas circulation space 80 before being introduced into said low-pressure duct 7.
  • the cooling enclosure 79 surrounds the gas regulator 78 and / or the heat source 12 and / or the hot gas inlet duct 19 in a sealed manner so that the working gas 81 cannot enter. in the gas circulation space 80 only through the enclosure inlet port 82, while said gas 81 can only leave said space 80 through the enclosure outlet port 83.
  • the enclosure inlet port 82 can be connected to the outlet of the gas regulator 78 by an enclosure inlet duct 84, the effective section of which is regulated by a flow control valve 85, the latter being able to - depending on its position - prohibit, leave free, or restrict the flow of the gas working 81 in said duct 84.
  • the enclosure outlet port 83 can be connected to the low-pressure regeneration duct 7 by an enclosure outlet duct 86, the effective section of which is regulated by a flow rate regulating valve 85, the latter being able to - as a function of its position - prohibit, leave free, or restrict the circulation of the gas working 81 in said enclosure outlet duct 86.
  • the figure 1 also illustrates that another variant of the regenerative cooling system 100 according to the invention consists in that the outlet of the gas regulator 78 can be connected to the low-pressure regeneration duct 7 by an enclosure bypass duct 87 which allows the working gas 81 expelled at the outlet of the gas regulator 78 to go directly from said outlet to the low-pressure regeneration duct 7 without passing through the gas circulation space 80.
  • the effective section of the enclosure bypass duct 87 can optionally be adjusted by a flow rate regulating valve 85, the latter being able - depending on its position - to prohibit, leave free, or restrict the flow of gas. working 81 in said bypass duct 87.
  • a heat shield 88 which can be made of any heat-insulating material known to those skilled in the art and which can - in addition to the enclosure cooling 79 - coat the various ducts and hot components that make up the regenerative heat engine 1.
  • said heat shield 88 is provided to prevent any excessive heat loss which is unfavorable to the efficiency of the regenerative heat engine 1.
  • the regeneration engine 1 here comprises a two-stage compressor 2 which consists in particular of a low-pressure compressor 35 which sucks in the gas working 81 in the atmosphere via a compressor inlet duct 3, the outlet of said compressor low-pressure 35 being connected to the inlet of a high-pressure compressor 36 via a compressor intercooler 37.
  • the figure 1 illustrates that at the outlet of the high-pressure compressor 36, the working gas 81 is expelled into the high-pressure regeneration duct 6 which comprises the regeneration heat exchanger 5 which in this case is a counter-current heat exchanger 41 known per se.
  • the working gas 81 is expelled from the high-pressure compressor 36 at a pressure of twenty bars and at a temperature of two hundred degrees Celsius.
  • the working gas 81 By circulating in the high-pressure regeneration duct 6, the working gas 81 is preheated to a temperature of six hundred and fifty degrees Celsius by the hot working gas 81 which circulates in the adjacent low-pressure regeneration duct 7.
  • the efficiency of the regeneration heat exchanger 5 is one hundred percent.
  • the working gas 81 which circulates in the low-pressure regeneration duct 7 enters the latter at a temperature of six hundred and fifty degrees Celsius and leaves said duct 7 at a temperature of two hundred degrees Celsius before be released into the atmosphere via the engine outlet duct 33, while the working gas 81 which circulates in the high-pressure regeneration duct 6 enters the latter at a temperature of two hundred degrees Celsius and leaves it at a temperature of two hundred degrees Celsius. temperature of six hundred and fifty degrees Celsius.
  • said working gas 81 is then superheated to one thousand four hundred degrees Celsius by the heat source 12 which - according to this exemplary embodiment - consists of a fuel burner 38.
  • the working gas 81 is conveyed through a hot gas inlet pipe 19 to the gas expander 78 which is none other than the expansion cylinder 13 of the heat engine with transfer-expansion and regeneration object of patent application N ° FR 15 51593 .
  • the hot gas inlet duct 19 is preferably made of ceramic with high temperature resistance until it is connected to an expansion cylinder head 14 covering one or the other end of the expansion cylinder 13.
  • the temperature of said duct 19 remains approximately equal to one thousand four hundred degrees Celsius so that the working gas 81 circulating in said duct 19 maintains its temperature throughout its journey.
  • each end of the expansion cylinder 13 is capped with an expansion cylinder head 14 so that with a double-acting pressure reducing piston 15 are defined two transfer-expansion chambers 16.
  • each cylinder head comprises a metering valve of intake 24 and an exhaust metering valve 31.
  • the heat transfer-expansion and regeneration engine being hot, the expansion cylinder 13 and the expansion cylinder heads 14 are maintained at a temperature in the region of seven hundred degrees Celsius. This makes it possible to produce said cylinder 13 and said cylinder heads 14 in a material that is less expensive and more common than ceramic, such as stainless steel or ferritic cast iron with silicon.
  • the double-acting expansion piston 15 is for its part, and according to this non-limiting example of embodiment of the regenerative cooling system 100 according to the invention, made of silicon nitride.
  • the average operating temperature of said piston 15 is of the order of eight hundred degrees Celsius.
  • said piston 15 is connected by mechanical transmission means 19 to a power output shaft 17, said means 19 being in particular constituted by a connecting rod 42 articulated around a crank 43.
  • the working gas 81 brought to a pressure of twenty bars and to a temperature of one thousand four hundred degrees Celsius is therefore introduced into one or the other transfer-expansion chamber 16 by the corresponding inlet metering valve 24.
  • said gas 81 begins to cool slightly, in particular in contact with the internal walls of the cylinder head 14 which it passes through, and the internal walls of the cylinder head.
  • the transfer-expansion chamber 16 into which it is introduced with the aim of being relaxed there by the double-acting pressure reducing piston 15. Said walls are - as we have seen previously - maintained at seven hundred degrees Celsius by the regenerative cooling system 100.
  • the double-acting regulator piston 15 having reached its Bottom Dead Center, the exhaust metering valve 31 opens and said piston 15 expels said gas 81 into the enclosure inlet duct 84 which conveys said gas 81 to speaker input port 82.
  • the working gas 81 then enters the gas circulation space 80 and then goes via this space to the enclosure outlet port 83. In doing so, said gas 81 licks the hot outer walls of the expansion cylinder 13 and the cylinder heads. expansion cylinder 14. Said outer walls have been provided wholly or partly rough and / or dotted with geometric patterns in order to produce a convective forcing forcing the working gas 81 to take more or less heat from said walls when said gas 81 circulates in contact with said walls.
  • the internal geometry of the cooling enclosure 79 and / or the external geometry of the expansion cylinder 13 and / or the external geometry of the expansion cylinder heads 14 can advantageously form channels which force all or part of the working gas 81 to following a route or several simultaneous routes to go from the enclosure entry port 82 to the enclosure exit port 83 via the gas circulation space 80.
  • the double strategy of convective forcing and forced route of the working gas 81 makes it possible to choose, first of all, the heat export zones from the hot external walls of the expansion cylinder 13 and the cylinder heads of the expansion cylinder 14 towards said gas 81, on the second hand, the chronological order of sweeping of said zones by said gas 81, and on the third and final part, the intensity of the convective forcing along the route of said gas 81.
  • the temperature of the working gas 81 subtracts heat from the hot outer walls of the expansion cylinder 13 and the expansion cylinder heads 14 to the point that the temperature of said gas 81 gradually goes from five hundred and fifty degrees Celsius to six hundred and fifty degrees Celsius. In doing so and in relation to the strategy of convective forcing and route chosen for said gas 81, the latter homogenizes the temperature of the expansion cylinder 13 and of the expansion cylinder heads 14, said temperature being maintained in the vicinity of seven hundred degrees Celsius.
  • the working gas 81 having reached its new temperature of six hundred and fifty degrees Celsius, said gas 81 arrives at the enclosure outlet port 83 and joins the low-pressure regeneration duct 7 via the enclosure outlet duct 86.
  • the heat extracted from the expansion cylinder 13 and the expansion cylinder heads 14 to maintain them at a temperature of the order of seven hundred degrees Celsius is in no way dissipated in vain.
  • said heat is reintroduced into the thermodynamic cycle of the regenerative heat engine 1 to replace part of the heat to be supplied by the fuel burner 38 to bring the working gas 81 to a temperature of one thousand four hundred. degrees Celsius before the latter is directed towards the expansion cylinder 13 and then introduced into the transfer-expansion chambers 16.
  • the enclosure bypass duct 87 which comprises a flow rate adjustment valve 85. It is also noted in figure 1 that the enclosure outlet duct 86 also comprises a flow rate adjustment valve 85.
  • These two said Valves 85 constitute an alternative embodiment of the regenerative cooling system 100 according to the invention and are provided to regulate the temperature of the expansion cylinder 13 and of the cylinder heads of the expansion cylinder 14.
  • the flow rate adjustment valve 85 of the enclosure bypass duct 87 opens said bypass duct 87 while the flow rate adjustment valve 85 of the enclosure outlet duct 86 closes said outlet duct 86.
  • This has the effect of preventing the working gas 81 expelled from the transfer-expansion chambers 16 by their respective exhaust metering valve 31 from passing through the exhaust space. circulation of gases 80 to reach the low-pressure regeneration duct 7. Said gas 81 therefore joins said duct 7 directly, via the enclosure bypass duct 87.
  • the flow rate control valves 85 are rarely either fully open or fully closed, and that said valves 85 can be kept ajar to regulate the temperature of the expansion cylinder 13 and of the expansion cylinder heads 14 without abrupt variation. working gas flow rate 81 circulating in the gas circulation space 80.
  • control device formed, for example, of at least one temperature sensor and a microcontroller known per se, which make it possible to control servomotors of any type whatsoever which each actuates a flow rate adjustment valve 85 on opening or closing.
  • the flow rate control valves 85 can also be connected to one another by a mechanical connection to share the same booster. In this case, said connection guarantees that when the first said valve 85 is closed the second is open, and vice versa.
  • the regenerative cooling system 100 provides numerous advantages, in particular to the use of the heat engine with transfer-expansion and regeneration which is the subject of patent application No. FR 15 51593 belonging to the applicant.
  • the pressure reducing cylinder 13 and the pressure reducing cylinder heads 14 from ceramic material such as, for example, silicon carbide. Indeed, this type of material is notoriously expensive to produce because of its great hardness making it difficult to machine using cutting tools or conventional rectification. Thanks to the regenerative cooling system 100 according to the invention, it is possible to replace said ceramic with cast iron or stainless steel. This greatly reduces the cost of manufacturing the heat transfer-expansion and regeneration engine, which is decisive, in particular for said engine to be able to access the automobile market.
  • the expansion cylinder 13 and the expansion cylinder heads 14 being cooler, it is possible to use materials with very low thermal conductivity and high mechanical resistance to compression such as quartz to produce the pillars.
  • the expansion valve cylinder heads 14 being maintained at seven hundred degrees Celsius, they can receive pre-existing silicon nitride valves, compatible with these temperature levels.
  • Such valves have for example been developed by the company "NGK” and have been the subject of research on their industrialization at low cost in particular within the framework of the project N ° G3RD-CT-2000-00248 entitled “LIVALVES”, financed in within the framework of the fifth European FP5-GROWTH framework program.
  • the air cushion segment as provided in patent application No. FR 15 51593 belonging to the applicant can be made of a superalloy which is durably resistant to these temperature levels, without risk for said segment of being subjected to a temperature significantly higher than said seven hundred degrees Celsius, in particular when the heat engine with transfer-expansion and regeneration is stopped and before the latter has cooled.
  • the regenerative cooling system 100 makes it possible to limit the temperature to which the heat shields 88 which surround the expansion cylinder 13 and the expansion cylinder heads 14.
  • the cooling enclosure 79 is inserted between between said screens 88 on the one hand, and said cylinder 13 and said cylinder heads on the other hand. The cost price and the durability of said screens 88 are thus improved to a considerable extent.
  • the regenerative cooling system 100 makes it possible to decouple the existing relationship according to patent application No. FR 15 51593 between the temperature resistance of the constituent materials of the expansion cylinder 13 and the expansion cylinder heads 14 on the one hand, and the temperature of the working gas 81 leaving the fuel burner 38 on the other hand.
  • the regenerative cooling system 100 can advantageously be applied to any other regenerative heat engine 1 whose configuration and temperature characteristics are compatible with said system 100.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (6)

  1. Regeneratives Kühlsystem (100), das für einen regenerativen Verbrennungsmotor (1) vorgesehen ist, wobei dieser Letztere mindestens einen regenerativen Wärmetauscher (5) aufweist, der eine Hochdruck-Regenerationsleitung (6) aufweist, in der ein Arbeitsgas (81) zirkuliert, um darin vorgewärmt zu werden, das zuvor von einem Kompressor (2) komprimiert worden ist, während das Gas (81) beim Austreten aus der Leitung (6) von einer Wärmequelle (12) überhitzt wird, bevor es in einen Gasdruckregler (78) eingeführt wird, in dem es entspannt wird, um eine Arbeit an einer Kraftabtriebswelle (17) zu erzeugen, wobei das Gas (81) dann am Ausgang des Gasdruckreglers (78) ausgestoßen wird und dann in eine Niederdruck-Regenerationsleitung (7) eingeführt wird, die der regenerative Wärmetauscher (5) aufweist, wobei das Gas (81) - indem es in der Leitung (7) zirkuliert - einen großen Teil seiner Restwärme an das Arbeitsgas (81) abgibt, das in der Hochdruck-Regenerationsleitung (6) zirkuliert, wobei das System (100) dadurch gekennzeichnet ist, dass es aufweist:
    • mindestens eine Kühlkammer (79), die den Gasdruckregler (78) und/oder die Wärmequelle (12) und/oder eine Einlassleitung der heißen Gase (19), die die Quelle (12) mit dem Regler (78) verbindet, ganz oder teilweise umgibt, während ein Raum zum Zirkulieren der Gase (80) zwischen der Kammer (79) einerseits und/oder dem Regler (78) und/oder der Quelle (12) und/oder der Leitung (19) andererseits gelassen wird,
    • mindestens eine Kammereintrittsöffnung (82), die direkt oder indirekt mit dem Ausgang des Gasdruckreglers (78) verbunden ist und durch die das gesamte oder ein Teil des Arbeitsgases (81), das von dem Regler (78) über den Ausgang ausgestoßen wird, in den Raum zum Zirkulieren der Gase (80) eindringen kann,
    • mindestens eine Kammeraustrittsöffnung (83), die direkt oder indirekt mit der Niederdruck-Regenerationsleitung (7) verbunden ist und über die das Arbeitsgas (81) aus dem Raum zum Zirkulieren der Gase (80) austreten kann, bevor es in die Niederdruckleitung (7) eingeführt wird.
  2. Regeneratives Kühlsystem nach Anspruch 1, dadurch gekennzeichnet, dass die Kammereintrittsöffnung (82) mit dem Ausgang des Gasdruckreglers (78) durch eine Kammereintrittsleitung (84) verbunden ist, deren tatsächlicher Querschnitt durch ein Durchflussregelventil (85) geregelt ist.
  3. Regeneratives Kühlsystem nach Anspruch 1, dadurch gekennzeichnet, dass die Kammeraustrittsöffnung (83) mit der Niederdruck-Regenerationsleitung (7) durch eine Kammeraustrittsleitung (86) verbunden ist, deren tatsächlicher Querschnitt durch ein Durchflussregelventil (85) geregelt ist.
  4. Regeneratives Kühlsystem nach Anspruch 1, dadurch gekennzeichnet, dass der Ausgang des Gasdruckreglers (78) durch eine Kammer-Bypass-Leitung (87) mit der Niederdruck-Regenerationsleitung (7) verbunden ist.
  5. Regeneratives Kühlsystem nach Anspruch 4, dadurch gekennzeichnet, dass der tatsächliche Querschnitt der Kammer-Bypass-Leitung (87) durch ein Durchflussregelventil (85) geregelt ist.
  6. Regeneratives Kühlsystem nach Anspruch 1, dadurch gekennzeichnet, dass die Außenseite der Kühlkammer (79) mit einer Wärmeabschirmung (88) verkleidet ist.
EP18707106.3A 2017-02-27 2018-02-12 Regeneratives kühlsystem Active EP3585993B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR1751571A FR3063311B1 (fr) 2017-02-27 2017-02-27 Systeme de refroidissement regeneratif
PCT/FR2018/050335 WO2018154214A1 (fr) 2017-02-27 2018-02-12 Système de refroidissement régénératif

Publications (2)

Publication Number Publication Date
EP3585993A1 EP3585993A1 (de) 2020-01-01
EP3585993B1 true EP3585993B1 (de) 2021-04-07

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Country Status (9)

Country Link
EP (1) EP3585993B1 (de)
JP (1) JP7065106B2 (de)
KR (1) KR102525744B1 (de)
CN (1) CN110234863B (de)
AU (1) AU2018225327B2 (de)
CA (1) CA3053015A1 (de)
ES (1) ES2874807T3 (de)
FR (1) FR3063311B1 (de)
WO (1) WO2018154214A1 (de)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
US12000357B2 (en) 2022-02-11 2024-06-04 Vianney Rabhi Reciprocating heat engine with hot cylinder head and cold cylinder

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Publication number Priority date Publication date Assignee Title
FR3094416B1 (fr) 2019-03-29 2021-03-05 Vianney Rabhi Plenum articulé
US11187184B2 (en) 2019-03-29 2021-11-30 Vianney Rabhi Articulated plenum for transfer-expansion-regeneration combustion engine
FR3132747B1 (fr) 2022-02-11 2024-01-05 Vianney Rabhi Piston à double effet multitemperature
FR3132737A1 (fr) 2022-02-11 2023-08-18 Vianney Rabhi Moteur thermique alternatif

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CN110234863B (zh) 2022-03-18
CN110234863A (zh) 2019-09-13
ES2874807T3 (es) 2021-11-05
FR3063311A1 (fr) 2018-08-31
EP3585993A1 (de) 2020-01-01
KR102525744B1 (ko) 2023-04-25
WO2018154214A1 (fr) 2018-08-30
CA3053015A1 (fr) 2018-08-30
AU2018225327B2 (en) 2024-01-04
JP7065106B2 (ja) 2022-05-11
FR3063311B1 (fr) 2019-07-19
KR20190116275A (ko) 2019-10-14
AU2018225327A1 (en) 2019-08-22
JP2020509282A (ja) 2020-03-26

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