EP3350433B1 - Doppeltwirkender expansionszylinder mit adaptivem träger - Google Patents

Doppeltwirkender expansionszylinder mit adaptivem träger Download PDF

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Publication number
EP3350433B1
EP3350433B1 EP16775804.4A EP16775804A EP3350433B1 EP 3350433 B1 EP3350433 B1 EP 3350433B1 EP 16775804 A EP16775804 A EP 16775804A EP 3350433 B1 EP3350433 B1 EP 3350433B1
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Prior art keywords
rod
cylinder
double
centering
pressure reducing
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EP16775804.4A
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English (en)
French (fr)
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EP3350433A1 (de
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Vianney Rabhi
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Individual
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Individual
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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
    • F02G1/04—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
    • 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
    • F02G2270/00—Constructional features
    • F02G2270/55—Cylinders

Definitions

  • the present invention relates to a dual-effect expansion cylinder with adaptive support, said cylinder being able to operate at high temperature and to be subjected to thermal expansions different from those of the transmission casing to which it is attached.
  • An engine with a piston regulator double effect is known in particular from the document EP1306539 .
  • volumetric regenerative engines inspired by turbocharged Brayton cycle engines, power turbine, burner and regenerator. These latter engines are the main source of power for certain gas-fired power plants or certain vessels such as those powered by the "Rolls-Royce WR-21" engine.
  • This engine differs from conventional regenerative Brayton cycle engines in that the normally used driving turbine is replaced by a regulator cylinder whose energy performance is maximized by intake and exhaust metering valves operating in a special mode described in the "operation" section of those applications.
  • the phasing of the intake metering valve maximizes the output of the expansion of the gases by extending the latter to the exhaust pressure.
  • the phasing of the exhaust metering valve is provided to re-compress the residual exhaust gas trapped in the dead volume found at the top dead center of the piston so that before the metering valve opens admission, the pressure and the temperature of said gases become equivalent to those of the gases leaving the burner. This last phasage avoids any irreversibility due to the discharge of gas under high pressure in a dead volume remained under low pressure.
  • the replacement of said power turbine by said expansion cylinder is in particular made possible by sealing means of innovative piston that prevents pressurized gases from leaking between said cylinder and the piston expander with which it cooperates.
  • sealing means of innovative piston that prevents pressurized gases from leaking between said cylinder and the piston expander with which it cooperates.
  • the said requests propose a layout and novel technical solutions that solve a technical problem hitherto unresolved, thus answering the identified and unmet need to make possible the production of regenerative engines of a much higher efficiency. to that of Brayton cycle engines with turbine regeneration, and far superior to that of Otto or Diesel internal combustion internal combustion engines of any type.
  • sealing means are in secondary claim to not exclude the possibility of other sealing means that would provide the same benefits.
  • the hot organs in order to preserve the maximum efficiency of the thermal machine, the hot organs must communicate as little heat as possible to the cold organs. This is decisive in the case, for example, of the heat transfer-expansion and regeneration engine which is the subject of patent applications no. 1550762 and no 1551593 owned by the applicant. Indeed, any heat transferred by the hot organs to the cold organs of said engine is irretrievably lost and can no longer be converted into motive power.
  • the fixing of hot parts carried at high temperature and subjected to high forces is preferably carried out by means of cold steel parts with high mechanical strength. This configuration should not result in excessive heat transfer from hot rooms to cold rooms.
  • the double-acting pressure-reducing cylinder with adaptive support according to the invention is in particular intended for high-temperature cylindrical piston-and-piston positive volumetric thermal machines, and to meet the triple need to take up high forces, to allow to different mechanically interconnected members and brought to different operating temperatures to expand and deform without compromising their operation, and limit heat transfer from hot rooms to cold rooms.
  • the double-acting pressure-reducing cylinder with adaptive support according to the invention is intended to facilitate the production of alternative machines whose cylinder (s) and piston (s) are for example brought to temperatures of the order of nine hundred to one thousand degrees Celsius. Such temperature results from the fact that the cylinder (s) and piston (s) compress and / or relax gas whose temperature may be of the order of one thousand one hundred to one thousand three hundred degrees Celsius, such temperatures being necessary to claim high thermodynamic yields.
  • the double-acting regulator cylinder with adaptive support is adaptable to any machine or apparatus equipped with (e) at least one cylinder operating or not at high temperature, said cylinder being connected to a housing or possibly a frame kept at a low temperature.
  • the transfer-expansion and regeneration thermal engine which is the subject of the French patent application Nos. 1550762 and no 1551593 , said requests belonging to the applicant.
  • the double-acting pressure reducing cylinder comprises at least one rod cooling tube which sealingly envelopes the pull rod over all or part of the length of said rod, a cooling fluid originating from a source of fluid cooling device which can circulate in a space left between the inner wall of said tube and the outer surface of said rod while the largest possible part of the surface external of said tube does not touch the inner wall of the rod tunnel so as to define with the latter wall empty space.
  • the double acting expansion cylinder of the present invention comprises at least a first tube supply port which communicates with the interior of the shaft cooling tube adjacent the first rod end, and / or at least a second port tubular supply which communicates with the inside of the rod cooling tube in the vicinity of the second rod end, the cooling fluid being able to circulate between said two orifices.
  • the double-acting pressure reducing cylinder comprises a rod cooling tube which comprises a tube flange held directly or indirectly clamped by the pulling rod or against an attachment lug which has the cylinder barrel or the upper yoke, against the transmission case.
  • the double-acting pressure reducing cylinder comprises a tube flange which is held tight by the pull rod against the fastening lug via a Banjo fitting which has at least one radial connection duct connected to the cooling fluid source on the one hand, and communicating with the inside of the stem cooling tube on the other hand.
  • the double-acting pressure-reducing cylinder comprises a heat-insulating riser which is interposed between the tube flange and the attachment lug, said riser being traversed right through its length along a tunnel of a riser in which is housed the traction rod and the rod cooling tube which surrounds it in a sealed manner while the greatest possible part of the outer surface of said tube does not touch the inner wall of the raising tunnel so as to define with this last wall an empty space.
  • the double-acting pressure reducing cylinder according to the present invention comprises a rod cooling tube which comprises at least one tube bulge consisting of an axial portion of said tube whose diameter is substantially equivalent or even slightly greater than that of the rod tunnel in which he is lodged.
  • the double-acting pressure reducing cylinder according to the present invention comprises a rod cooling tube which comprises at least one tube diameter restriction consisting of an axial portion of said tube whose diameter is substantially equivalent to or even slightly less than that of the body of the tube. pull rod.
  • the double-acting pressure reducing cylinder according to the present invention comprises a shaft cooling tube which has at least one radial communication hole which allows the cooling fluid to enter or escape from said tube.
  • the double-acting pressure reducing cylinder comprises a traction rod which is hollow to form an internal rod cooling channel arranged in the length of said rod, said channel emerging axially or radially from said rod while a fluid of cooling from a source of cooling fluid can flow in said channel.
  • the double-acting pressure reducing cylinder comprises a pressure chamber which is connected to a source of pressurized air and which is fixed to the centering gantry or arranged on or in the latter while an upper piston rod which extends the double-acting expander piston on the side of the upper hot gas chamber passes through the upper yoke via an upper stem orifice formed in said cylinder head and via an access port to the chamber passing through the centering gantry to open into the pressure chamber so that the end of said rod which is furthest from said piston is still immersed in said chamber regardless of the position of said piston.
  • the double-acting pressure reducing cylinder comprises a transmission casing which is capped with a centering and sealing plate pierced with an access orifice to the transmission means through which the lower piston rod passes to be connected to the transmission means, said plate being rigidly fixed on said housing.
  • the double-acting pressure reducing cylinder comprises a chamber access port which cooperates with or has rod sealing means which provide a seal between said port and the upper piston rod.
  • the double-acting pressure reducing cylinder according to the present invention comprises an access port to the transmission means which cooperates with or has rod sealing means which provide a seal between said port and the lower piston rod.
  • the double-acting pressure reducing cylinder comprises rod sealing means which comprise an upper stem seal and a lower stem seal sufficiently far apart to form between said two seals, an oil-circulating chamber into which a cooling-lubricating oil supply duct opens and from which a cooling-lubricating oil outlet duct is released.
  • the double-acting pressure reducing cylinder of the present invention comprises rod sealing means which cooperate with a rod guide ring housed inside or outside the oil circulation chamber.
  • the double-acting pressure reducing cylinder comprises lower cylinder centering means and / or upper cylinder centering means which consist of a centering elastic disk which can be drilled in the center of a disk hole. through which the lower piston rod or an upper piston rod passes respectively, while its periphery constitutes a disk fixing flange sealingly fixed respectively to the transmission casing and / or the centering gantry.
  • the double-acting pressure reducing cylinder comprises a centering and sealing plate which carries the lower centering means of the cylinder, which consist of a resilient centering disc whose periphery forms a fixed disc fixing collar. sealingly on said platen, said disk being pierced at its center with a disk hole through which the lower piston rod passes without touching said disk, the edge of the disk hole having a circular contact pad which is kept in contact sealing with a centering and sealing cone that has the lower yoke, said cone being male or female, and the contact between said pad and said cone having the effect of axially deforming and from its center the elastic centering disk.
  • the double-acting pressure-reducing cylinder comprises upper centering means of the cylinder which consist of an elastic centering disk whose periphery forms a disk-fixing flange sealingly fixed to the centering gantry, said disk being pierced at its center with a disk hole whose edge has a circular contact pad which is kept in sealing contact with a centering and sealing cone which has the upper yoke, said cone being male or female, and the contact between said pad and said cone having the effect of axially deforming and from its center the elastic centering disk.
  • the double-acting expander cylinder 1 comprises a cylinder barrel 71 cooperating with a double-acting expander piston 2 which is connected by a lower piston rod 46 to transmission means 3 which may for example be constituted by a connecting rod 4 articulated around a crank 5 which is arranged on a crankshaft 6, said connecting rod 4 being connected to the double-acting expander piston 2 directly by a piston pin or indirectly via a butt 7.
  • said means 3 could also consist of a cam, a hydraulic transmitting pump, an electricity generator or any other transmission means known to those skilled in the art.
  • the transmission means 3 are housed in a transmission casing 8 maintained at low temperature on which is fixed the cylinder barrel 71, the latter and the double-acting expander piston 2 being able to operate at high temperature.
  • the end of the cylinder drum 71 which opens on the side of said means 3 is closed by a lower yoke 9 which passes through the lower piston rod 46 via a lower rod orifice 51 to define with the double-acting expansion piston 2 a lower hot gas chamber 11 while the other end of said barrel 71 is closed by an upper yoke 10 to define with said piston 2 an upper hot gas chamber 12,
  • the lower yoke 9 and the upper yoke 10 may comprise at least one valve 50 controlled by a valve actuator 70.
  • the double-acting regulator cylinder 1 with adaptive support comprises at least one hollow pillar 13 traversed from one side to the other by its length by a rod tunnel 14 which can be either completely closed or perforated .
  • a first pillar end 15 of the hollow pillar 13 rests directly or indirectly on the transmission casing 8 while a second pillar end 16 of the pillar 13 directly or indirectly supports the cylinder drum 71, the lower cylinder head 9 and the upper yoke 10.
  • the double-acting pressure reducing cylinder 1 with an adaptive support provides that the first end of the pillar 15 can pivot about a ball joint 42 and / or bend relative to said casing 8 while the second end of the pillar 16 can pivot about a ball joint 42 and / or bend with respect to said cylinder barrel 71, the pivoting of said ends 15, 16 can take place either by means of a mechanical connection of pivot or cardan type or a ball joint 42, either by flexing all or part of the hollow pillar 13, or by both.
  • the hollow abutment 13 may be made of zirconium dioxide called “zirconia", this ceramic offering good mechanical strength at high temperature, low thermal conductivity, and a coefficient of expansion close to that of steel.
  • the latter can rest on the second end of pillar 16 approximately to the height of the double-acting piston expander 2 when the latter is positioned at half of its stroke.
  • the lower yoke 9 and the upper yoke 10 move away approximately the same distance from the center position of the double-acting expander piston 2 .
  • the double-acting pressure reducing cylinder 1 with an adaptive support comprises at least one traction rod 17 housed in the rod tunnel 14, a first rod end 18 of said traction rod 17 being directly or indirectly secured to the transmission housing 8 while a second rod end 19 of said pull rod 17 is secured to the cylinder drum 71 and / or to the lower yoke 9 and / or to the upper yoke 10, said first end 18 being pivotable around a ball joint 42 and / or bend relative to said casing 8 while said second end 19 can pivot about a ball joint 42 and / or bend relative to said cylinder 1.
  • pivoting of said ends 18, 19 can be effected either by means of a mechanical connection of pivot or cardan type or of a ball joint 42, or by the flexion of all or part of the traction rod 17, either by both.
  • the second rod end 19 can pass through an ear hole 24 that includes a lug 25 that has said barrel 71 and / or said yokes 9, 10, while either a rod head 28 or a stem nut 26 screwed onto a rod thread 29 provided on the pull rod 17 bears on said lug 25 so as to grip the latter between said head 28 or said nut 26, and the hollow pillar 13.
  • first rod end 18 can be secured to the transmission casing 8 also by means of a rod head 28 or a stem nut 26 screwed onto a rod thread 29.
  • said stem thread 29 can be screwed into a thread 27 directly or indirectly in the transmission housing 8.
  • a compression spring can be inserted either between the rod head 28 or the stem nut 26 and the attachment lug 25, or between said head 28 or any other threaded part in which is screwed the rod thread 29, and any other support piece.
  • Said compression spring may consist for example of one or more washer (s) "Belleville”.
  • Such a compression spring can in particular limit the tension to which the pull rod 17 is subjected when the various members that it keeps tightly together expand under the effect of their rise in temperature.
  • the cylinder drum 71, the lower yoke 9 and the upper yoke 10 must preferably be covered with at least one heat shield which limits the heat emissions of said members 71, 9 and 10 into the environment.
  • said screen may for example consist of several layers of thin metal sheets having pins that leave between each said sheet a blade of air, or be made of any other arrangement specific to heat shields and known to the man of art.
  • the pull rod 17 can be juxtaposed with the hollow pillar 13 which in this case may not be traversed from one side in the direction of its length by a rod tunnel 14 while the function of said rod 17 and said pillar 13 remains unchanged and that the ball joints 42 with which cooperates said rod 17 and said pillar 13 produce the same effects.
  • the double-acting expander cylinder 1 comprises lower centering means of the cylinder 20 positioned in the vicinity of the lower yoke 9, said means 20 bearing on the cylinder drum 71 or the lower yoke 9 firstly, and directly or indirectly on the transmission case 8 of the second part, and said means 20 leaving the cylinder barrel 71 free to move parallel to its longitudinal axis relative to the transmission case 8, but prohibiting said barrel 71 to move in the plane perpendicular to said axis, always with respect to said casing 8.
  • the double-acting regulator cylinder 1 also comprises upper means for centering the cylinder 21 positioned in the vicinity of the upper yoke 10, said means 21 bearing on the cylinder drum 71 or the upper yoke 10 first part, and on a centering gantry 22 rigidly fixed to the transmission housing 8 and maintained at a height close to that of the upper yoke 10 by at least one rigid portal pillar 23 of the second part, said means 21 leaving the cylinder barrel 71 free to move parallel to its longitudinal axis relative to the transmission casing 8, but prohibiting said barrel 71 to move in the plane perpendicular to said axis, always with respect to said casing 8.
  • the figures 4 and 5 show at least one rod cooling tube 30 that can comprise the double-acting pressure reducing cylinder 1 according to the invention, said tube 30 sealingly enveloping the traction rod 17 over all or part of the length of said rod 17, a coolant 31 from a source of cooling fluid 40 able to circulate in a space left between the inner wall of said tube 30 and the outer surface of said rod 17, while the largest possible part of the external surface of said tube 30 does not touch the inner wall of the rod tunnel 14 so as to define with the latter wall empty space.
  • the double-acting pressure reducing cylinder 1 may comprise at least a first tube supply port 32 communicating with the inside of the shaft cooling tube 30 in the vicinity of the first rod end 18, and / or at least a second tube supply port 33 communicating with the inside of the rod cooling tube 30 in the vicinity of the second rod end 19, the cooling fluid 31 being able to circulate between the said two orifices 32, 33 however said fluid 31 is colder when it enters the rod cooling tube 30 than when it comes out.
  • a fluid pump not shown can be provided to force the cooling fluid 31 to circulate in the rod cooling tube 30, said pump can continue to operate for some time after stopping the heat engine at which applies the double-acting expander cylinder 1 according to the invention.
  • the shaft cooling tube 30 may comprise a tube flange 34 held directly or indirectly clamped by the pull rod 17 either against an attachment lug 25 that has the cylinder barrel 71 or the upper cylinder head 10, or against transmission case 8.
  • the tube flange 34 can be held tight by the traction rod 17 against the attachment lug 25 via a Banjo coupling 38 which comprises at least one radial connection duct 39 connected to the source of cooling fluid 40 on the one hand, and communicating with the inside of the rod cooling tube 30 on the other hand.
  • radial connecting duct 39 may be connected to the source of cooling fluid 40 or to other radial connecting ducts 39 which Banjo 38 comprises of other stem cooling tubes 30 by means of a flexible or deformable conduit that can accommodate variations in distance induced by the thermal expansion of the various members that constitute the double-acting regulator cylinder 1 according to the invention.
  • a heat insulating riser 68 may be inserted between the tube flange 34 and the attachment lug 25, said riser 68 being traversed throughout its length direction by a raising tunnel 69 in which is housed the pull rod 17 and the rod cooling tube 30 which tightly surrounds it while the largest possible part of the external surface of said tube 30 does not touch the inner wall of the raising tunnel 69 so as to define with this last wall an empty space.
  • thermal insulation riser 68 can advantageously be made of a material resistant to high temperatures and having a low thermal conductivity such as zirconium dioxide.
  • the rod cooling tube 30 may comprise at least one tube bulge 35 consisting of an axial portion of said tube 30 whose diameter is substantially equivalent or even slightly greater than that of the rod tunnel 14 in which it is housed, thus ensuring said tube 30 remains locally centered in said tunnel 14, and if necessary achieving a seal between said tube 30 and said tunnel 14.
  • the rod cooling tube 30 may further include at least one tube diameter restriction 36 consisting of an axial portion of said tube 30 whose diameter is substantially equivalent to or even slightly less than that of the body of the pull rod 17 in order to locally perform a seal between said tube 30 and said rod 17.
  • the rod cooling tube 30 may also comprise at least one radial communication hole 37 which allows the cooling fluid 31 to penetrate into said tube 30, or to escape from it.
  • the pull rod 17 may be hollow to form an internal rod cooling channel arranged in the length of said rod 17, said channel opening axially or radially from said rod 17 while a cooling fluid 31 from a source of cooling fluid 40 can flow in said channel.
  • the double-acting expander cylinder 1 may comprise a pressure chamber 44 connected to a source of pressurized air 45 and which is fixed on the centering gantry 22 or fitted on or in the latter while an upper piston rod 47 which extends the double-acting expander piston 2 on the side of the upper hot gas chamber 12 passes through the upper yoke 10 via an upper stem orifice 43 provided in said cylinder head 10 and via an orifice access to the chamber 52 passing through the centering gantry 22 to open into the pressure chamber 44 so that the end of said rod 47 which is furthest from said piston 2 always remains immersed in said chamber 44 whatever the position said piston 2.
  • This particular configuration of the double-acting pressure reducing cylinder 1 according to the invention makes it possible, for example, to supply compressed air - in particular via the pressure chamber 44 and an internal channel that comprises the upper piston rod 47 - sealing means 48.
  • the means 48 possibly being similar or identical to those described in the French patent applications no. 1550762 and no 1551593 belonging to the applicant and allowing the realization of a thermal engine transfer-relaxation and regeneration.
  • the transmission casing 8 may be capped with a centering and sealing plate 53 pierced with an access orifice to the transmission means 54 through which the lower piston rod 46 passes to be connected. to the transmission means 3, said plate 53 being rigidly fixed to said housing 8 by screws or by any other means known to those skilled in the art. Alternatively, said plate 53 may form an integral part of said casing 8.
  • chamber access port 52 may cooperate with, or include, shaft sealing means 55 which provide a seal between said port 52 and the upper piston rod 47.
  • FIGS. 2 , 3 and 6 illustrate that the access port to the transmission means 54 may cooperate with - or comprise - rod sealing means 55 which provide a seal between said port 54 and the lower piston rod 46.
  • rod seal means 55 may comprise a top shank seal 56 and a lower shank seal 57 sufficiently remote from each other to - between the two said seals 55 seals 56, 57 - an oil-flow chamber 58 into which a cooling-lubricating oil supply pipe 59 opens and from which a cooling-lubricating oil outlet pipe 60 leaves.
  • the oil flow chamber 58 has the dual function of lubricating and cooling the lower piston rod 46 and / or the upper piston rod 47.
  • the upper rod seal 56 and / or the lower rod seal 57 may consist in particular of a section segment or two superimposed section segments and whose sections are angularly offset while the outer surface of the lower piston rod 46 and / or the upper piston rod 47 may be provided with shallow double-helix stripes which form a succession of oil tanks and hydrodynamic lift surfaces.
  • segment (s) constituting the upper rod seal 56 can be kept at a distance from those constituting the lower rod seal 57 by a segment spacer spring 61 also designed - in particular because it includes orifices or passages for passing the flow of cooling and lubricating oil established between the coolant-lubrication supply line 59 and the coolant-lubrication oil outlet conduit 60.
  • the rod sealing means 55 can cooperate with a rod guiding ring 62 housed inside or outside the oil circulation chamber 58, said ring 62 being made of bronze or in any another material usually used to manufacture bearings or antifriction and / or hydrodynamic rings, while said ring 62 provides radial guidance of the lower piston rod 46 in the access port to the transmission means 54 and / or the rod upper piston 47 in the access port to the chamber 52.
  • the rod sealing means 55 are preferably provided with a rod guide ring 62 when they apply to the upper piston rod 47 while the radial guide of the lower piston rod 46 is provided by said butt 7 alone.
  • the lower centering means of the cylinder 20 and / or the upper centering means of the cylinder 21 may consist of an elastic centering disk 63 being pierceable at its center with a disk hole 64 through which the lower piston rod 46 or an upper piston rod 47 respectively passes, while its periphery constitutes a fixed disk mounting collar 65 of sealing manner respectively on the transmission casing 8 and / or on the centering gantry 22.
  • the centering and sealing plate 53 can carry the lower centering means of the cylinder 20 which consist of a resilient centering disc 63 whose periphery forms a disc fixing flange 65 sealingly attached to said platen 53, said disk 63 being pierced at its center with a disk hole 64 through which the lower piston rod 46 passes without touching said disk 63, the edge of the disk hole 64 having a circular contact pad 67 which is maintained in sealing contact with a centering and sealing cone 66 that has the lower yoke 9, said cone 66 being male or female, and the contact between said slider 67 and said cone 66 having the effect of deforming axially and from its center the centering elastic disk 63.
  • the disc fixing flange 65 can be fixed to the centering and sealing plate 53 by means of at least one screw, a clip, or any other fastening means known to the person skilled in the art. art. It is noted that advantageously, the centering elastic disk 63 may be made of a material resistant to high temperatures and having a low thermal conductivity such as zirconium dioxide.
  • centering elastic disk 63 can be fixed on the lower cylinder 9 while the centering and sealing cone 66 is arranged on or in the centering and sealing plate 53.
  • the upper centering means of the cylinder 21 may consist of a resilient centering disc 63 whose periphery forms a disc fixing flange 65 sealingly attached to the centering gantry 22, said disc 63 being drilled in its center a disk hole 64 whose edge has a circular contact pad 67 which is kept in sealing contact with a centering and sealing cone 66 that has the upper yoke 10, said cone 66 being male or female, and the contact between said shoe 67 and said cone 66 having the effect of axially deforming and from its center the resilient centering disc 63.
  • disc fixing flange 65 can be fixed to the centering gantry 22 by means of at least one screw, a clip, or any other fastening means known to those skilled in the art.
  • the resilient centering disk 63 may be made of a material resistant to high temperatures and having a low thermal conductivity such as zirconium dioxide.
  • the resilient centering disk 63 may be attached to the upper yoke 10 while the centering and sealing cone 66 is provided on or in the centering gantry 22.
  • a contact pad similar to that which is present the disk hole 64 can be arranged respectively on the lower yoke 9 or on the upper yoke 10 while a centering and sealing cone similar to that presented by said yokes 9, 10 is arranged on and / or in the centering elastic disk 63.
  • the resilient centering disc 63 may consist, for example, of a split or non-slotted torus of steel or of a superalloy, of an expandable washer which may or may not consist of multiple folds stacked radially. and made of the same piece of metal or ceramic, at least three spring-biased needles, distributed every one hundred and twenty degrees and cooperating with a sealing segment, and generally, of any technical solution capable of ensure centering and sealing in the desired functional conditions while limiting heat leakage from any warm room to any cold room.
  • the double-acting expander cylinder 1 applies to the heat transfer-expansion and regeneration engine of which the French patent application no. 1550762 and no 1551593 belong to the applicant.
  • This application has an exemplary value and does not exclude any other use of the double-acting regulator cylinder 1 according to the invention.
  • the cylinder barrel 71 of the double-acting expander cylinder 1 according to the invention rises rapidly in temperature with respect to the transmission casing 8 on which it is fixed, said casing 8 accommodating the transmission means 3.
  • the double-acting expansion piston 2 which cooperates with said barrel 71, as well as for the lower yoke 9 which closes the end of the barrel 71 on the side of the transmission means 3, and for the upper yoke 10 which closes the barrel. other end of the barrel 71.
  • the transmission means 3 are provided for transforming the reciprocating movements that takes place in the cylinder drum 71 the double-acting expansion piston 2, in continuous rotational movement of a crankshaft 6.
  • said means 3 consist of a connecting rod 4 connected to the double acting expansion piston 2 by through a butt 7, said rod 4 being articulated around a crank 5 arranged on the crankshaft 6.
  • the high temperature of said barrel 71, said piston 2, and said cylinder heads 9, 10 is necessary to give the heat transfer-expansion and regeneration engine the best possible efficiency, while the relatively low temperature maintenance of the transmission casing 8 and the means of transmission 3 is necessary for the latter to maintain a high mechanical strength and for the lubrication of the various components that constitute them is possible without risk of coking of any lubricating oil.
  • the cylinder barrel 71, the double-acting expander piston 2, the lower yoke 9 and the upper yoke 10 are for example mainly made of silicon carbide which has a high mechanical strength at high temperature, whereas the crankcase transmission 8 can be made of aluminum and the transmission means 3 can be made of cast iron or steel.
  • silicon carbide Although the coefficient of thermal expansion of silicon carbide is lower than that of aluminum or steel, components at nine hundred degrees Celsius expand more than those worn at only one hundred degrees Celsius. It is therefore necessary to let the silicon carbide components expand freely compared to those made of aluminum, cast iron or steel without inducing excessive mechanical stress in silicon carbide or other materials. .
  • each hollow pillar 13 has two ball joints 42 around which it articulates.
  • zone “D" of said figure 5 that between the first pillar end 15 of said pillar 13 and the transmission casing 8 is intercalated a first ball joint 42 while the "C” zone of the same figure 5 shows that between the second pillar end 16 of said pillar 13 and the lower yoke 9 is intercalated a second ball joint 42.
  • each hollow pillar 13 is traversed from one end to the other by its length by a rod tunnel 14 in which is housed a traction rod 17.
  • a rod tunnel 14 in which is housed a traction rod 17.
  • the first rod end 18 of the traction rod 17 is secured to the transmission housing 8 via a first ball joint 42.
  • the "A" zone of the figure 5 illustrates that the second rod end 19 is indirectly secured to the upper yoke 10 via a second ball joint 42.
  • the second rod end 19 of the pull rod 17 has a rod head 28 which holds the barrel drum 71, the lower yoke 9 and the upper yoke 10 compressed together between said head 28 and the hollow pillar 13.
  • the "B" and “C” zones of the figure 5 illustrate this provision in a particularly obvious way.
  • the figures 4 and 5 show that the first rod end 18 of the pull rod 17 terminates - according to this non-limiting embodiment - by a thread of rod 29 screwed into a thread 27 formed in a ball joint 42 which bears in the housing of transmission 8 and around which articulates said first end 18.
  • the various ball joints 42 around which the four recessed pillars 13 and the traction rod 17 with which they cooperate allow the cylinder barrel 71, the lower yoke 9 and the upper yoke 10 to expand freely. This is done, however, that the recessed pillars 13 can transmit the tensile and compressive forces between the cylinder drum 71, the lower yoke 9 and the upper yoke 10 first, and the second transmission case 8.
  • the centering and sealing plate 53 and the centering gantry 22 which are rigidly secured to the transmission casing 8 each bear and respectively the lower centering means of the cylinder 20 and the upper centering means of the cylinder 21, said lower means 20 and upper 21 being each constituted by a resilient centering disc 63.
  • the elastic centering disc 63 which constitutes the lower centering means of the cylinder 20 is particularly visible in figure 6 while that constituting the upper centering means of the cylinder 21 is particularly visible in figure 7 .
  • the purpose of the elastic centering disks 63 is to ensure centering and orientation relative to the transmission casing 8 of the rigid assembly formed by the cylinder drum 71, the lower yoke 9 and the upper yoke 10.
  • said disc 63 is sealingly fixed by its disc fixing flange 65 on the centering and sealing plate 53 by means of eight fastening screws which are counted in figure 4 .
  • said disk 63 is pierced at its center with a disk hole 64 through which the lower piston rod 46 passes without touching said disk 63, the edge of the disk hole 64 having a circular male contact pad 67 which is maintained in sealing contact with the centering and sealing cone 66 female that has the lower yoke 9.
  • the latter exerts a force on said pad 67 which deforms axially and from its center the centering elastic disk 63 relative to its rest position.
  • the contact between the male conical shape of the contact pad 67 and the female conical shape of the centering and sealing cone 66 tends to center the bottom yoke 9 on the centering and sealing plate 53.
  • said contact provides a seal which prevents the pressurized gases contained in the lower hot gas chamber 11 from escaping from said chamber 11.
  • the axial deformation of the centering elastic disk 63 does not compromise the integrity of the latter, which deforms in its elastic range.
  • the conical shape of the centering and sealing cone 66 and the contact pad 67 accommodates differential expansions between these two parts 66, 67 regardless of the direction of said expansions.
  • the lower centering means of the cylinder 20 and the upper centering means of the cylinder 21 cooperate to keep the cylinder drum 71 always centered around the piston double-acting expander 2, and always parallel thereto.
  • said means 55 also ensure the cooling of the lower piston rod 46 by means of an oil circulation chamber 58 into which a cooling-lubricating oil supply pipe 59 opens and from which a cooling oil-lubricating output duct 60. It is easy to notice that the flow of oil flowing between said ducts 59, 60 being in permanent contact with the lower piston rod 46, said flow makes it possible to maintain said rod 46 at a temperature for example slightly above one hundred degrees Celsius, but not higher.
  • the upper shaft seal 56 consists of two superimposed cutting segments whose sections are angularly offset while the lower rod seal 57 consists of a single sectional segment, the two said seals 56, 57 being held apart from each other by a segment spacer spring 61 which includes orifices allowing the flow of coolant and lubricating oil to pass between the cooling oil supply line and lubrication 59 and the coolant-lubrication oil outlet conduit 60, via the oil flow chamber 58.
  • the figure 7 illustrates the same arrangement, with the main difference that the segment spacer spring 61 gives way to a rod guide ring 62 which provides radial guidance of the upper piston rod 47 which, according to the non-limiting example taken here to illustrate the operation of the double-acting expander cylinder 1 according to the invention, opens into the pressure chamber 44 arranged in the centering gantry 22 and which we saw in description that it can supply compressed air via an internal channel that comprises the upper piston rod 47 sealing means 48 such as a continuous ring perforated air cushion 49 housed in a segment groove arranged at the periphery of the double acting expansion piston piston 2.
  • the oil pump that supplies the oil circulation chambers 58 continues to supply the latter with oil to cool the lower piston rod 46 and the upper piston rod 47 and this, as long as the lower yoke 9 and the upper yoke 10 continue to transmit heat to said chambers 58 and may carry the oil contained in said chambers 58 at temperature of coking.
  • the particular configuration of the double-acting pressure reducing cylinder 1 according to the invention strongly limits the heat transfer from the Bottom yoke 9 to the transmission housing 8. Recall that said transfer adversely affects the efficiency of the heat transfer-expansion and regeneration engine.
  • the recessed pillars 13 are not only of great length as illustrated in FIG. Figures 1 to 5 , but they are also preferably made of a low thermal conductivity material such as zirconium oxide.
  • each pillar comprises a rod cooling tube 30 which tightly surrounds said traction rod 17 with which it co-operates over a majority of the length of said rod 17.
  • a cooling fluid 31 from a source of cooling fluid 40 flows in the space left between the inner wall of said tube 30 and the outer surface of said rod 17, however that as much as possible of the outer surface of said tube 30 does not touch the inner wall of the rod tunnel 14 so as to define with the latter wall a void space which constitutes a thermal insulation.
  • zone “ A” of the figure 5 the rod cooling tube 30 has a tube bulge 35 which ensures that said tube 30 remains locally centered in the rod tunnel 14. It is further seen in zone “D” and in the vicinity of the first rod end 18 that two further tube bulges 35 each constitute both a centering and a seal between said tube 30 and said tunnel 14. Said two other bulges 35 cooperate with a tube diameter restriction 36 which locally provides a seal between the rod cooling tube 30 and the pull rod 17.
  • the stem cooling tube 30 has a first tube supply port 32 located between said two further bulges 35, said first port 32 communicating with the interior of the stem cooling tube 30 in the vicinity of the first end of the tube.
  • rod 18 on the one hand and being connected to the forward circuit of the cooling fluid source 40 via channels arranged in the transmission case 8 on the other hand.
  • the rod cooling tube 30 terminates - at the second rod end 19 - by a tube flange 34 held tight by the rod head 28 against a thermal insulation riser 68 interposed between said flange 34 and the attachment lug 25 of the upper yoke 10.
  • a Banjo coupling 38 is interposed between the rod head 28 and said flange 34, said coupling 38 comprising a radial connecting duct 39 connected to the return circuit of the coolant source 40 on the one hand, and communicating with the inside of the stem cooling tube 30 on the other hand via the end of the stem cooling tube 30 which receives the collar of tube 34.
  • thermal insulation riser 68 - preferably made of zirconium oxide - constitutes an additional obstacle to the transfer of heat from the upper yoke 10 carried to about nine hundred degrees Celsius towards the rod head 28 maintained at only one hundred degrees Celsius .
  • this particular configuration which makes it possible to cool the traction rod 17 is useless if it is made of a high temperature resistant material such as "zirconia", silicon carbide, alumina or any superalloy specifically developed for this type of use.

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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)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Pressure Vessels And Lids Thereof (AREA)
  • Actuator (AREA)

Claims (19)

  1. Doppeltwirkender Expansionszylinder (1) mit adaptivem Träger, aufweisend eine Zylinderlaufbahn (71), die mit einem doppeltwirkenden Expansionskolben (2) zusammenwirkt, der durch eine untere Kolbenstange (46) mit Getriebemitteln (3) verbunden ist, die in einem Getriebegehäuse (8) aufgenommen sind, auf dem die Zylinderlaufbahn (71) befestigt ist, während das Ende der Laufbahn (71), das auf der Seite der Mittel (3) mündet, durch einen unteren Zylinderkopf (9) geschlossen wird, den die untere Kolbenstange (46) über eine untere Stangenöffnung (51) durchquert, um mit dem doppeltwirkenden Expansionskolben (2) eine untere Heißgaskammer (11) zu definieren, während das andere Ende der Laufbahn (71) durch einen oberen Zylinderkopf (10) geschlossen wird, um mit dem Kolben (2) eine obere Heißgaskammer (12) zu bilden, dadurch gekennzeichnet, dass er umfasst:
    • mindestens eine ausgehöhlte Stütze (13), die in Richtung ihrer Länge vollständig von einem Stangentunnel (14) durchquert wird, wobei ein erstes Stützenende (15) der Stütze (13) direkt oder indirekt auf dem Getriebegehäuse (8) ruht, während ein zweites Stützenende (16) der Stütze (13) direkt oder indirekt die Zylinderlaufbahn (71), den unteren Zylinderkopf (9) und den oberen Zylinderkopf (10) trägt, wobei das erste Ende (15) um eine Gelenkverbindung (42) schwenken und/oder in Bezug auf das Gehäuse (8) nachgeben kann, während das zweite Ende (16) um eine Gelenkverbindung (42) schwenken und/oder in Bezug auf die Zylinderlaufbahn (71) nachgeben kann;
    • mindestens eine Zugstange (17), die in dem Stangentunnel (14) aufgenommen ist, wobei ein erstes Stangenende (18) der Zugstange (17) direkt oder indirekt am Getriebegehäuse (8) befestigt ist, während ein zweites Stangenende (19) der Zugstange (17) direkt an der Zylinderlaufbahn (71) und/oder am unteren Zylinderkopf (9) und/oder am oberen Zylinderkopf (10) befestigt ist, wobei das erste Ende (18) um eine Gelenkverbindung (42) schwenken und/oder in Bezug auf das Gehäuse (8) nachgeben kann, während das zweite Ende (19) um eine Gelenkverbindung (42) schwenken und/oder in Bezug auf den Zylinder (1) nachgeben kann;
    • untere Zentriermittel des Zylinders (20), die in der Nähe des unteren Zylinderkopfes (9) angeordnet sind, wobei die Mittel (20) auf der Zylinderlaufbahn (71) oder dem unteren Zylinderkopf (9) einerseits und direkt oder indirekt auf dem Getriebegehäuse (8) andererseits zur Anlage kommen und die Mittel (20) die Zylinderlaufbahn (71) sich frei parallel zu ihrer Längsachse in Bezug auf das Getriebegehäuse (8) bewegen lassen, aber die Laufbahn (71) daran hindern, sich in der senkrecht zu dieser Achse verlaufenden Ebene, ebenfalls in Bezug auf das Gehäuse (8), zu bewegen;
    • obere Zentriermittel des Zylinders (21), die in der Nähe des oberen Zylinderkopfes (10) angeordnet sind, wobei die Mittel (21) auf der Zylinderlaufbahn (71) oder dem oberen Zylinderkopf (10) einerseits und auf einem Zentrierjoch (22), das starr am Getriebegehäuse (8) befestigt ist und von mindestens einer starren Jochstütze (23) in einer ähnlichen Höhe wie der obere Zylinderkopf (10) gehalten wird, andererseits zur Anlage kommen, wobei die Mittel (21) die Zylinderlaufbahn (71) sich frei parallel zu ihrer Längsachse in Bezug auf das Getriebegehäuse (8) bewegen lassen, aber die Laufbahn (71) daran hindern, sich in der senkrecht zu dieser Achse verlaufenden Ebene, ebenfalls in Bezug auf das Gehäuse (8), zu bewegen.
  2. Doppeltwirkender Expansionszylinder nach Anspruch 1, dadurch gekennzeichnet, dass er mindestens ein Stangenkühlrohr (30) aufweist, das die Zugstange (17) über die gesamte oder einen Teil der Länge der Stange (17) auf dichte Weise umgibt, wobei ein von einer Kühlmittelquelle (40) kommendes Kühlmittel (31) in einem Raum, der zwischen der Innenwand des Rohrs (30) und der Außenfläche der Stange (17) gelassen wird, zirkulieren kann, wobei der größtmögliche Anteil der Außenfläche des Rohrs (30) die Innenwand des Stangentunnels (14) nicht berührt, so dass er mit dieser letzten Wand einen leeren Raum definiert.
  3. Doppeltwirkender Expansionszylinder nach Anspruch 2, dadurch gekennzeichnet, dass er mindestens eine erste Rohrzuleitungsöffnung (32), die mit dem Innenraum des Stangenkühlrohrs (30) kommuniziert, in der Nähe des ersten Stangenendes (18) und/oder mindestens eine zweite Rohrzuleitungsöffnung (33), die mit dem Innenraum des Stangenkühlrohrs (30) kommuniziert, in der Nähe des zweiten Stangenendes (19) aufweist, wobei das Kühlmittel (31) zwischen diesen beiden Öffnungen (32, 33) zirkulieren kann.
  4. Doppeltwirkender Expansionszylinder nach Anspruch 2, dadurch gekennzeichnet, dass das Stangenkühlrohr (30) einen Rohrflansch (34) aufweist, der direkt oder indirekt durch die Zugstange (17) entweder gegen ein Befestigungsohr (25), welche die Zylinderlaufbahn (71) oder der obere Zylinderkopf (10) aufweist, oder gegen das Getriebegehäuse (8) eingespannt gehalten wird.
  5. Doppeltwirkender Expansionszylinder nach Anspruch 4, dadurch gekennzeichnet, dass der Rohrflansch (34) durch die Zugstange (17) gegen das Befestigungsohr (25) über eine Schwenkverschraubung (38), die mindestens einen radialen Anschlusskanal (39) aufweist, der mit der Kühlmittelquelle (40) einerseits verbunden ist und mit dem Innenraum des Stangenkühlrohrs (30) andererseits kommuniziert, eingespannt gehalten wird.
  6. Doppeltwirkender Expansionszylinder nach Anspruch 4, dadurch gekennzeichnet, dass ein Wärmeisolierungsaufsatz (68) zwischen dem Rohrflansch (34) und der Befestigungsohr (25) angeordnet ist, wobei der Aufsatz (68) in Richtung seiner Länge vollständig von einem Aufsatztunnel (69) durchquert wird, in dem die Zugstange (17) aufgenommen ist und das Stangenkühlrohr (30), dass sie auf dichte Weise umgibt, wobei der größtmögliche Teil der Außenfläche des Rohrs (30) die Innenwand des Aufsatztunnels (69) nicht berührt, so dass mit dieser letzten Wand ein leerer Raum definiert wird.
  7. Doppeltwirkender Expansionszylinder nach Anspruch 2, dadurch gekennzeichnet, dass das Stangenkühlrohr (30) mindestens eine Rohrausbauchung (35) aufweist, die aus einem axialen Abschnitt des Rohrs (30) besteht, dessen Durchmesser im Wesentlichen gleichwertig oder sogar geringfügig größer als der des Stangentunnels (14) ist, in dem er aufgenommen ist.
  8. Doppeltwirkender Expansionszylinder nach Anspruch 2, dadurch gekennzeichnet, dass das Stangenkühlrohr (30) mindestens eine Rohrdurchmesserverengung (36) aufweist, die aus einem axialen Abschnitt des Rohrs (30) besteht, dessen Durchmesser im Wesentlichen gleichwertig oder sogar geringfügig kleiner als der des Körpers der Zugstange (17) ist.
  9. Doppeltwirkender Expansionszylinder nach Anspruch 2, dadurch gekennzeichnet, dass das Stangenkühlrohr (30) mindestens ein radiales Verbindungsloch (37) aufweist, das es dem Kühlmittel (31) ermöglicht, in das Rohr (30) einzudringen oder daraus zu entweichen.
  10. Doppeltwirkender Expansionszylinder nach Anspruch 1, dadurch gekennzeichnet, dass die Zugstange (17) hohl ist, um einen inneren Stangenkühlkanal zu bilden, der in der Länge der Stange (17) ausgebildet ist, wobei der Kanal axial oder radial der Stange (17) mündet, während ein von einer Kühlmittelquelle (40) kommendes Kühlmittel (31) in dem Kanal zirkulieren kann.
  11. Doppeltwirkender Expansionszylinder nach Anspruch 1, dadurch gekennzeichnet, dass eine mit einer Druckluftquelle (45) verbundene Druckkammer (44) auf dem Zentrierjoch (22) befestigt oder auf oder in diesem ausgebildet ist, während eine obere Kolbenstange (47), die den doppeltwirkenden Expansionskolben (2) auf der Seite der oberen Heißgaskammer (12) verlängert, den oberen Zylinderkopf (10) über eine obere Stangenöffnung (43), die in dem Zylinderkopf (10) ausgebildet ist, und über eine Zugangsöffnung zu der das Zentrierjoch (22) durchqueren Kammer (52) durchquert, um in die Druckkammer (44) zu münden, so dass das Ende der Stange (47), das am weitesten vom Kolben (2) entfernt ist, unabhängig von der Position des Kolbens (2) immer in die Kammer (44) eingetaucht bleibt.
  12. Doppeltwirkender Expansionszylinder nach Anspruch 1, dadurch gekennzeichnet, dass das Getriebegehäuse (8) von einer Zentrier- und Abdichtplatte (53) bedeckt wird, die mit einer Zugangsöffnung zu den Getriebemitteln (54) durchbohrt ist, durch welche die untere Kolbenstange (46) verläuft, um mit den Getriebemitteln (3) verbunden zu werden, wobei die Platte (53) starr an dem Gehäuse (8) befestigt ist.
  13. Doppeltwirkender Expansionszylinder nach Anspruch 11, dadurch gekennzeichnet, dass die Zugangsöffnung zur Kammer (52) mit Stangendichtmitteln (55) zusammenwirkt - oder solche aufweist -, die eine Abdichtung zwischen der Öffnung (52) und der oberen Kolbenstange (47) ausführen.
  14. Doppeltwirkender Expansionszylinder nach Anspruch 12, dadurch gekennzeichnet, dass die Zugangsöffnung zu den Getriebemitteln (54) mit Stangendichtmitteln (55) zusammenwirkt - oder solche aufweist -, die eine Abdichtung zwischen der Öffnung (54) und der unteren Kolbenstange (46) ausführen.
  15. Doppeltwirkender Expansionszylinder nach Anspruch 13 oder 14, dadurch gekennzeichnet, dass die Stangendichtmittel (55) eine obere Stangenabdichtung (56) und eine untere Stangenabdichtung (57) umfassen, die ausreichend weit voneinander entfernt sind, um - zwischen den beiden Abdichtungen (56, 57) - eine Ölzirkulationskammer (58) zu bilden, in die ein Kühl-/Schmieröleinlasskanal (59) mündet und von der ein Kühl-/Schmierölauslasskanal (60) abgeht.
  16. Doppeltwirkender Expansionszylinder nach Anspruch 15, dadurch gekennzeichnet, dass die Stangendichtmittel (55) mit einem Stangenführungsring (62) zusammenwirken, der innerhalb oder außerhalb der Ölzirkulationskammer (58) aufgenommen ist.
  17. Doppeltwirkender Expansionszylinder nach Anspruch 1, dadurch gekennzeichnet, dass die unteren Zentriermittel des Zylinders (20) und/oder die oberen Zentriermittel des Zylinders (21) aus einer elastischen Zentrierscheibe (63) bestehen, die in ihrem Mittelpunkt mit einem Scheibenloch (64) durchbohrt sein kann, durch das hindurch die untere Kolbenstange (46) bzw. eine obere Kolbenstange (47) verläuft, während ihr Umfang einen Scheibenbefestigungsflansch (65) bildet, der auf dichte Weise auf dem Getriebegehäuse (8) und/oder auf dem Zentrierjoch (22) befestigt ist.
  18. Doppeltwirkender Expansionszylinder nach Anspruch 12, dadurch gekennzeichnet, dass die Zentrier- und Dichtplatte (53) die unteren Zentriermittel des Zylinders (20) trägt, die aus einer elastischen Zentrierscheibe (63) bestehen, deren Umfang einen Scheibenbefestigungsflansch (65) bildet, der auf dichte Weise auf der Platte (53) befestigt ist, wobei die Scheibe (63) in ihrem Mittelpunkt mit einem Scheibenloch (64) durchbohrt ist, durch das hindurch die untere Kolbenstange (46) verläuft, ohne die Scheibe (63) zu berühren, wobei der Rand des Scheibenlochs (64) einen kreisförmigen Kontaktschuh (67) aufweist, der in dichtem Kontakt mit einem Zentrier- und Dichtkegel (66) gehalten wird, den der untere Zylinderkopf (9) aufweist, wobei der Kegel (66) männlich oder weiblich sein kann, und der Kontakt zwischen dem Schuh (67) und dem Kegel (66) bewirkt, das die elastische Zentrierscheibe (63) axial und von ihrem Mittelpunkt aus verformt wird.
  19. Doppeltwirkender Expansionszylinder nach Anspruch 1, dadurch gekennzeichnet, dass die oberen Zentriermittel des Zylinders (21) aus einer elastischen Zentrierscheibe (63) bestehen, deren Umfang einen Scheibenbefestigungsflansch (65) bildet, der auf dichte Weise auf dem Zentrierjoch (22) befestigt ist, wobei die Scheibe (63) in ihrem Mittelpunkt mit einem Scheibenloch (64) durchbohrt ist, dessen Rand einen kreisförmigen Kontaktschuh (67) aufweist, der in dichtem Kontakt mit einem Zentrier- und Dichtkegel (66) gehalten wird, den der obere Zylinderkopf (10) aufweist, wobei der Kegel (66) männlich oder weiblich sein kann, und der Kontakt zwischen dem Schuh (67) und dem Kegel (66) bewirkt, das die elastische Zentrierscheibe (63) axial und von ihrem Mittelpunkt aus verformt wird.
EP16775804.4A 2015-09-14 2016-09-07 Doppeltwirkender expansionszylinder mit adaptivem träger Active EP3350433B1 (de)

Applications Claiming Priority (2)

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FR1558585A FR3041040B1 (fr) 2015-09-14 2015-09-14 Cylindre detendeur a double effet a support adaptatif
PCT/FR2016/052232 WO2017046479A1 (fr) 2015-09-14 2016-09-07 Cylindre detendeur a double effet a support adaptatif

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Cited By (1)

* Cited by examiner, † Cited by third party
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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10704431B2 (en) 2017-10-03 2020-07-07 Vianney Rabhi Regenerative valve hydraulic actuator
US11255319B2 (en) * 2019-03-09 2022-02-22 Neo Mechanics Limited Shaft-cylinder assembly for high temperature operation
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

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3775973A (en) * 1970-05-04 1973-12-04 P Hudson Combustion products pressure generators intermittent burner cycle and engines
US4307997A (en) * 1979-05-08 1981-12-29 The United States Of America As Represented By The United States Department Of Energy Free piston inertia compressor
IT1203452B (it) * 1987-04-07 1989-02-15 Tiziana Rigolli Motore rotativo a combustione interna,a pistoni assiali
US6968688B2 (en) * 2001-10-24 2005-11-29 Enerlyt Potsdam Gmbh Two-cycle hot-gas engine
US7137366B2 (en) * 2004-09-10 2006-11-21 Tgs Innovations, Lp Two-cycle swash plate internal combustion engine
CN102182582B (zh) * 2011-03-22 2014-05-07 杨永顺 外燃机及其传动机构

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Cited By (1)

* Cited by examiner, † Cited by third party
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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CA2998581A1 (fr) 2017-03-23
ES2751760T3 (es) 2020-04-01
FR3041040B1 (fr) 2017-11-03
KR20180052657A (ko) 2018-05-18
KR102675206B1 (ko) 2024-06-13
FR3041040A1 (fr) 2017-03-17
WO2017046479A1 (fr) 2017-03-23
CA2998581C (fr) 2023-12-12
JP6876035B2 (ja) 2021-05-26
AU2016321973B2 (en) 2020-07-02
CN108138694A (zh) 2018-06-08
AU2016321973A1 (en) 2018-04-19
EP3350433A1 (de) 2018-07-25
CN108138694B (zh) 2020-11-06
JP2018530697A (ja) 2018-10-18

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