• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
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    • 专利摘要:
    The double-acting expansion cylinder (1) comprises a cylinder barrel (71) which cooperates with a double-acting expansion piston (2) connected to transmission means (3) housed in a transmission casing (8), while a hollow pillar (13) whose ends are articulated is traversed by a rod tunnel and bears on said housing (8) to support said barrel (71), a pull rod (17) also articulated through said tunnel to tighten the cylinder barrel (71) on the hollow abutment (13) while lower centering means of the cylinder (20) and upper centering means of the cylinder (21) integral with the transmission casing (8) in particular via a gantry crane centering (22) allow the cylinder barrel (71) free to move parallel to its longitudinal axis but not in the plane perpendicular to said axis.
    公开号:FR3041040A1
    申请号:FR1558585
    申请日:2015-09-14
    公开日:2017-03-17
    发明作者:Vianney Rabhi
    申请人:Vianney Rabhi；
    IPC主号:
    专利说明:

    DOUBLE EFFECT RETRACTOR CYLINDER WITH ADAPTIVE SUPPORT
    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.
    It would be of great energy interest to make 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.
    It should be noted that the applicant holds two French patent applications relating to a heat transfer-expansion and regeneration engine. The first of these requests was registered on January 30, 2015 under the number 1550762, and the second is dated February 25, 2015 and bears the number 1551593.
    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.
    In particular, the phasing of the intake metering valve maximizes the output of the expansion of the gases by extending the latter to the exhaust pressure. In addition, 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.
    According to said applications, the replacement of said power turbine by said expansion cylinder is in particular made possible by innovative piston sealing means which prevent the pressurized gases from escaping between said cylinder and the expansion piston with which it cooperates. These last two bodies being brought to a very high temperature, they exclude any recourse to any oil lubrication whether of a segment or a ring and any contact between the hot regulating cylinder on the one hand, and a segment or a seal on the other hand. This is why the innovative sealing means proposed in patent applications No. 1550762 and No. 1551593 make it possible to overcome any need for lubrication and contact by maintaining an air film interposed between a ring. perforated continuous and the expander cylinder, the flow of said air further ensuring the cooling of said ring.
    By the same token, 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.
    It is noted that in the applications No. 1550762 and No. 1551593, the sealing means are in secondary claim not to exclude the possibility of other sealing means that would provide the same benefits.
    Having said this, whether it be the expansion cylinder as presented in applications Nos. 1550762 and 1551593, or any other expansion cylinder or not, since said cylinder operates at a high temperature, it must be constituted - as well as the cylinder head (s) which closes (s) the end (s) and the piston with which it cooperates - a material with sufficiently high mechanical strength at high temperature such as alumina, silicon carbide or zirconium oxide. Certain grades of stainless steel or superalloys may also be used. However, their mechanical strength compared to their cost does not necessarily make the most judicious choice.
    The problem is that these bodies and materials brought to temperatures near one thousand degrees Celsius or more cooperate with other organs whose operating temperature remains significantly lower, of the order of one hundred degrees Celsius only. Among said other members are for example the mechanical power transmission means to which the piston is connected, or the casing which encloses said means and on which is directly or indirectly fixed the cylinder - regulator or not - and its cylinder head (s) ).
    It is thus necessary to make possible the cooperation between these different organs which are connected or fixed between them, which operate at different temperatures, and which are possibly made of materials whose coefficient of thermal expansion is different.
    In particular, it is necessary that the forces produced by the gas pressure on the piston single or double effect can be collected by the mechanical transmission means so that they can deliver the work in a usable form. Said gases applying the same forces on the cylinder head (s) closing the cylinder, said same forces must be taken over by a mechanical connection interposed between the one or more yoke (s) and the casing which encloses the mechanical means of transmission. While each fulfilling their function, these different organs must be able to freely expand and deform in a homogeneous manner or not.
    It should also be noted that 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 transfer-expansion and regeneration thermal engine which is the subject of patent applications Nos. 1550762 and 1551593 belonging to 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.
    However, 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. This is why 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 the various members mechanically connected to each other and brought to different operating temperatures to expand and deform without compromising their operation, and to limit heat transfer from hot rooms to cold rooms.
    In addition, 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.
    In the field of application of reciprocating thermal machines with piston (s) in general and heat engines in particular, it results from the invention a double-acting expansion cylinder with adaptive support: • Whose isotropic or anisotropic expansion may be different of that of the transmission casing on which is fixed and this, without compromising neither the operation of said cylinder nor that of the piston which evolves in said cylinder, and without significantly altering the volumetric ratio of any engine or any thermal machine of which it is one of the constituents; • Which always remains centered on the piston with which it cooperates, despite the fact that the latter can also be heated to high temperature and be connected to transmission means operating at low temperature, just like the transmission housing in which they are housed and on which is fixed said cylinder; • Which can be securely fastened - as well as its cylinder head (s) - on the transmission case by means of steel connections with high mechanical strength and this, despite the low temperature required by said steel to maintain its strength, and despite the high temperature to which said cylinder and its cylinder head (s) are subjected; • Which exports little of its heat to the cold parts with which it cooperates, which preserves the efficiency of any engine or thermal machine of which it is one of the constituents; • The material (s) of which it is constituted is (are) subjected to a moderate temperature gradient which gives the said material (s) (x) a high resistance and a great durability.
    It is understood that the double-acting regulator cylinder with adaptive support according to the invention 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. By way of non-limiting example, among the examples of application of said invention is the transfer-expansion and regeneration thermal engine which is the subject of French patent applications Nos. 1550762 and 1551593, said applications belonging to the applicant.
    The other features of the present invention have been described in the description and in the dependent claims directly or indirectly dependent on the main claim.
    The double-acting, adaptive-support expansion cylinder comprises a cylinder barrel cooperating with a double-acting expansion piston which is connected by a lower piston rod to transmission means housed in a transmission casing on which the cylinder barrel is fixed. , while the end of said barrel which opens on the side of said means is closed by a lower yoke which passes through the lower piston rod via a lower rod orifice to define with the double-acting pressure reducing piston a lower hot gas chamber while the other end of said barrel is closed by an upper yoke to define with said piston a higher hot gas chamber, and comprises according to the invention: • At least one hollow pillar traversed from one end to the other by its length by a rod tunnel, a first pillar end of said pillar resting directly or indirectly on the transmitting housing ission while a second pillar end of said pillar directly or indirectly supports the barrel drum, the lower yoke and the upper yoke, while said first end can pivot about a ball joint and / or bend relative to said casing while said second end is pivotable about a ball joint and / or bent with respect to said cylinder barrel; At least one pull rod housed in the rod tunnel, a first rod end of said pull rod being directly or indirectly secured to the transmission housing while a second rod end of said pull rod is secured to the shaft; cylinder and / or bottom yoke and / or upper yoke, said first end being pivotable about a ball joint and / or bent with respect to said housing while said second end is pivotable about a ball joint and / or flex with respect to said cylinder; Lower cylinder centering means positioned in the vicinity of the lower yoke, said means being supported on the cylinder drum or the lower cylinder first part, and directly or indirectly on the second transmission casing, and said means leaving the barrel of free cylinder to move parallel to its longitudinal axis relative to the transmission housing, but prohibiting said drum to move in the plane perpendicular to said axis, always with respect to said housing; • Upper centering means of the cylinder positioned in the vicinity of the upper yoke, said means bearing on the cylinder drum or the upper yoke of the first part, and on a centering gantry rigidly fixed to the transmission housing and maintained at a height adjacent to that of the upper yoke by at least one rigid pillar gantry second part, said means allowing the cylinder barrel free to move parallel to its longitudinal axis relative to the transmission housing, but prohibiting said drum to move in the plane perpendicular to said axis, always with respect to said housing.
    The double-acting pressure reducing cylinder according to the present invention 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 that 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 outer surface of said tube does not touch the inner wall of the stem tunnel so as to define with this last wall an 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 which includes - rod sealing means which provide a seal between said port and the lower piston rod.
    The double-acting pressure reducing cylinder according to the present invention 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 according to the present invention 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 according to the present invention 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 according to the present invention 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 following description with reference to the accompanying drawings and given by way of non-limiting example will better understand the invention, the features it has, and the benefits it is likely to provide:
    Figure 1 is a three-quarter view of the double-acting pressure reducing cylinder according to the invention, and the transmission housing on which it is fixed.
    FIG. 2 is a three-dimensional front and cutaway view of the double-acting pressure-reducing cylinder according to the invention, said view also showing the transmission casing to which the cylinder barrel is attached, as well as the double-acting pressure-reducing piston and the means for transmission housed in said housing, said means being according to this embodiment consisting of a rod articulated on a crank connected to a crankshaft, and a butt.
    Figure 3 is a schematic longitudinal section of the double-acting pressure reducing cylinder according to the invention according to an alternative embodiment identical to that shown in Figure 2.
    FIGS. 4 is an exploded three-dimensional view of the double-acting pressure reducing cylinder according to the invention, and according to a variant embodiment identical to that presented in FIG.
    FIG. 5 is a side view of the double-acting pressure reducing cylinder according to the invention, showing by means of a section the particular configuration of the hollow pillar, of the pulling rod and of the various ball joints with which these two members cooperate, said section being enlarged and sectioned in the right portion of said figure for ease of understanding.
    FIG. 6 is a diagrammatic sectional view of the centering and sealing plate of the double-acting pressure-reducing cylinder according to the invention, of the elastic centering disc, and rod sealing means, the latter cooperating with the lower stem of FIG. piston.
    Figure 7 is a schematic sectional view of a portion of the centering gantry of the double-acting pressure reducing cylinder according to the invention, the elastic centering disc fixed on said gantry, and rod sealing means which cooperate with the rod upper piston which opens - according to this particular embodiment - in a pressure chamber. DESCRIPTION OF THE INVENTION
    FIGS. 1 to 7 show the double-acting regulator cylinder 1 with adaptive support, various details of its components, its variants, and its accessories.
    As clearly shown in FIGS. 2 to 4, 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 can for example consist of 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 stick 7.
    It will be noted that, alternatively, 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.
    Note that - as illustrated in Figures 1 to 5, 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 piston expander double effect 2 can operate at high temperatures.
    It is noted, again in FIGS. 1 to 5, that the end of the cylinder barrel 71 which opens on the side of said means 3 is closed by a lower yoke 9 through which the lower piston rod 46 passes via a lower stem 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 cylinder head 9 and the upper yoke 10 may comprise at least one valve 50 controlled by a valve actuator 70.
    FIGS. 1 to 5 also show that the double-acting pressure reducing cylinder 1 with an adaptive support according to the invention comprises at least one hollow pillar 13 traversed from one end to the other by its length by a rod tunnel 14 which can be either totally closed, openwork.
    It can be seen that 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.
    In addition, the double-acting pressure reducing cylinder 1 with an adaptive support according to the invention 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.
    According to a particular embodiment of the double-acting expander cylinder 1 according to the invention, 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.
    Note that advantageously, to prevent the volumetric ratio of the lower hot gas chamber 11 and the upper hot gas chamber 12 does not vary too much during the heating of the cylinder barrel 71, the latter can be based on the second pillar end 16 approximately at the height of the double-acting piston expander 2 when the latter is positioned at half its stroke. Thus, when the cylinder barrel 71 expands under the effect of its rise in temperature, 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 .
    FIGS. 1 to 5 also illustrate that the double-acting pressure reducing cylinder 1 with an adaptive support according to the invention comprises at least one traction rod 17 housed in the rod tunnel 14, a first rod end 18 of said pull rod 17 being directly or indirectly secured to the transmission casing 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, first end 18 pivotable about 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.
    It is noted that the 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.
    Note that to be secured to the cylinder barrel 71 and / or said cylinder heads 9, 10, 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.
    It should be noted that the 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. Alternatively, said stem thread 29 can be screwed into a thread 27 directly or indirectly in the transmission housing 8.
    According to a particular embodiment of the double-acting expander cylinder 1 according to the invention, 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. In all cases, advantageously, 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.
    It is noted that as technical equivalent and variant of the double-acting regulator cylinder 1 according to the invention, 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.
    FIGS. 2, 3, 4 and 6 clearly show that the double-acting expander cylinder 1 according to the invention comprises lower centering means of the cylinder 20 positioned in the vicinity of the lower yoke 9, said means 20 being supported on the cylinder barrel 71 or the lower cylinder 9 firstly, and directly or indirectly on the second transmission casing 8, and said means 20 leaving the cylinder barrel 71 free to move parallel to its longitudinal axis relative to the housing transmission 8, but prohibiting said drum 71 to move in the plane perpendicular to said axis, always with respect to said housing 8.
    FIGS. 2, 3, 4 and 7 illustrate that the double-acting regulator cylinder 1 according to the invention also comprises upper cylinder centering means 21 positioned in the vicinity of the upper yoke 10, said means 21 being supported on the barrel of the cylinder. cylinder 71 or the upper yoke 10 first, 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 pillar gantry 23 of the second part said means 21 leaving the cylinder barrel 71 free to move parallel to its longitudinal axis with respect to the transmission casing 8, but preventing said barrel 71 from moving in the plane perpendicular to said axis, always with respect to said casing 8.
    FIGS. 4 and 5 show at least one rod cooling tube 30 that may 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 cooling fluid 31 coming from a source of cooling fluid 40 able to circulate in a space left between the inner wall of said tube 30 and the external surface of said rod 17 while the greatest possible part of the surface external 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.
    FIGS. 4 and 5 specify that the double-acting expander cylinder 1 according to the invention may comprise at least a first tube supply port 32 communicating with the inside of the stem cooling tube 30 in the vicinity of the first end of the tube. rod 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 two said orifices 32, 33 while said fluid 31 is colder when it enters the rod cooling tube 30 than when it leaves.
    Note that 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.
    This last arrangement makes it possible, for example, to evacuate the heat that the cylinder barrel 71 and its cylinder heads 9, 10 are likely to continue to transmit during their cooling to the pull rod 17. It should also be noted that once out of the rod cooling tube 30, the cooling fluid 31 can be cooled by a heat exchanger before being reintroduced into said tube 30, or renewed.
    Still in Figures 4 and 5, it is noted that the rod cooling tube 30 may comprise a tube flange 34 held directly or indirectly clamped by the pull rod 17 is against a lug 25 that has the cylinder drum 71 or the upper yoke 10, or against the transmission case 8.
    According to a particular variant embodiment of the double-acting pressure reducing cylinder 1 according to the invention, 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.
    It will be noted that the 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.
    As can be seen in FIGS. 1 to 5, a thermal insulation riser 68 may be interposed between the tube flange 34 and the attachment lug 25, said extension 68 being traversed right through its length along its length. a raising tunnel 69 in which is housed the traction rod 17 and the rod cooling tube 30 which tightly surrounds it while the largest possible part of the outer surface of said tube 30 does not touch the inner wall of the tunnel raises 69 so as to define with the latter wall an empty space.
    It is noted that the 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.
    FIGS. 4 and 5 show that 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 this guaranteeing that said tube 30 remains locally centered in said tunnel 14, and realizing if necessary 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.
    It will also be noted that, as illustrated in FIGS. 4 and 5, the stem 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. . As a variant not shown, it will be noted that 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.
    FIGS. 2, 3 and 7 clearly show that the double-acting pressure reducing cylinder 1 according to the invention may comprise a pressure chamber 44 connected to a source of pressurized air 45 and which is fixed on the centering gantry 22 or arranged 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 yoke 10 and via an access port 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 remains always immersed in said chamber 44 regardless of the position of 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. such as a perforated continuous air-cushion ring 49 housed in a segment groove arranged at the periphery of the double-acting expander piston 2, said 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 heat transfer engine-relaxation and regeneration.
    In FIGS. 1 to 4 and in FIG. 6, it is illustrated that 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 passes the lower piston rod 46 to be connected to the transmission means 3, said plate 53 being rigidly fixed on 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.
    In FIGS. 2, 3 and 7, it will be noted that the access orifice to the chamber 52 can cooperate with or comprise rod sealing means 55 which seal between said orifice 52 and the upper piston rod. 47.
    Similarly, FIGS. 2, 3 and 6 illustrate that the access orifice to the transmission means 54 can cooperate with or comprise rod sealing means 55 which seal between said orifice 54 and the rod. In FIGS. 6 and 7, illustrated in the most convincing manner, the rod seal means 55 may comprise a rod upper seal 56 and a lower rod seal 57 sufficiently far apart. one of the other to form - between the two said seals 56, 57 - an oil flow chamber 58 into which opens a supply duct for cooling-lubricating oil 59 and from which a duct cooling-lubricating oil outlet 60.
    It is noted in said figures that 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. It is further noted that 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.
    In FIG. 6, it can be seen that the 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 - to pass the flow of cooling and lubricating oil between the cooling oil-lubricating supply line 59 and the cooling-lubricating oil outlet duct 60.
    In FIG. 7, it can be seen that the rod sealing means 55 can cooperate with a rod guide ring 62 housed inside or outside the oil circulation chamber 58, said ring 62 being made of bronze or in any other 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 of the upper piston rod 47 in the access orifice to the chamber 52.
    Note also that if the transmission means 3 comprise a butt 7, 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.
    In FIGS. 2 to 4 and in FIGS. 6 and 7, it will be noted that according to a particular configuration of the double-acting expander cylinder 1 according to the invention, the lower centering means of the cylinder 20 and / or the upper centering means of the cylinder 21 may consist of a resilient centering disc 63 pierceable at its center with a disk hole 64 through which the lower piston rod 46 or an upper piston rod 47 passes respectively while its periphery constitutes a collar of disc fixing 65 fixed in a sealed manner respectively to the transmission casing 8 and / or the centering gantry 22.
    FIGS. 2 to 4 and FIG. 6 show that the centering and sealing plate 53 may carry the lower centering means of the cylinder 20, which consist of an elastic centering disc 63 whose periphery forms a collar for fixing the disk 65 sealingly attached to said plate 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 kept 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 pad 67 and said cone 66 having the effect of axially deforming and from its center the centering elastic disk 63.
    It should be noted that 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.
    Alternatively, the 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.
    Similarly, it will be noted in FIGS. 2 to 4 and in FIG. 7 that the upper centering means of the cylinder 21 may consist of a resilient centering disc 63 whose periphery forms a disk-fixing flange 65 sealingly attached. on the centering gantry 22, said disk 63 being pierced at its center with 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 is present the upper yoke 10, 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 elastic centering disk 63.
    It should be noted that the 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.
    Note also that if the double-acting expander piston 2 is extended - on the side of the upper hot gas chamber 12 - by an upper piston rod 47, the latter passes through the disc hole 64 without touching the elastic centering disk 63 .
    It will further be appreciated that advantageously, 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.
    Alternatively, 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.
    It may also be noted that, as an alternative to what has just been described and whether it is the lower centering means of the cylinder 20 or the upper centering means of the cylinder 21, 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.
    It will be noted that, by way of a variant, 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, 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. OPERATION OF THE INVENTION:
    The operation of the double-acting regulator cylinder 1 with adaptive support according to the invention is easily understood in the light of FIGS. 1 to 7.
    To detail said operation, it will be assumed here that the double-acting expander cylinder 1 applies to the transfer-expansion and regeneration heat engine of which the French patent applications Nos. 1550762 and 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.
    When said engine starts, 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 same applies to 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.
    FIGS. 2 and 3 show that, according to the particular embodiment of the double-acting expander cylinder 1 according to the invention which is exposed to it, the transmission means 3 are provided for transforming the back-and-forth movements that performs in the cylinder drum 71 the double-acting expander piston 2, in continuous rotational movement of a crankshaft 6. For these purposes and still according to this non-limiting example, said means 3 consist of a connecting rod 4 connected to the piston double effect expander 2 through a butt 7, said rod 4 being articulated around a crank 5 arranged on the crankshaft 6.
    It will be assumed here that the temperature of the cylinder barrel 71, the double-acting expander piston 2, the lower yoke 9 and the upper yoke 10 reaches, for example, nine hundred degrees Celsius, whereas the temperature of the transmission casing 8 and the means transmission 3 that hosts remains limited to one hundred degrees Celsius.
    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 transmission means 3 is necessary for the latter to maintain a high mechanical strength and for the lubrication of the various members that constitute them is possible without risk of coking of any lubricating oil.
    It should be noted that 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.
    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. .
    This must be possible while ensuring that the forces applied to the double-acting expansion piston 2 by the pressure alternately prevailing in the lower hot gas chamber 11 and then in the upper hot gas chamber 12 are well transmitted by the lower piston rod 46 to the connecting rod 4 via the buttstock 7.
    It should be noted that said efforts tend to move the drum barrel 71 away from the transmission casing 8 when the gas pressure is high in the upper hot gas chamber 12, the double-acting pressure-reducing piston 2 exerting a compression force of comparable intensity on the rod 4, while said efforts tend to bring said barrel 71 of said casing 8 when the pressure of the gas is high in the lower hot gas chamber 11 said piston 2 exerting a tensile force of comparable intensity on the rod 4. C is to resume these tensile and compressive forces applied to the cylinder barrel 71 and more precisely lower yoke 9 and the upper yoke 10 with which it cooperates, that said barrel 71 is connected to the transmission housing 8 by hollowed pillars 13 shown in Figures 1 to 5 and which are - by way of non-limiting example - four in number as can easily be counted in Figure 4.
    As illustrated particularly clearly in Figure 5, each hollow pillar 13 has two ball joints 42 around which it articulates. It is noted in zone "D" of said FIG. 5 that between the first pillar end 15 of said pillar 13 and the transmission casing 8 a first ball joint 42 is inserted while the zone "C" of the same FIG. that between the second pillar end 16 of said pillar 13 and the lower yoke 9 is intercalated a second ball joint 42.
    FIG. 5 also shows that each hollow pillar 13 is traversed right through its length by a rod tunnel 14 in which a traction rod 17 is housed. As illustrated in zone "D" of said FIG. 5, the first rod end 18 of the traction rod 17 is secured to the transmission casing 8 via a first ball joint 42. The zone "A" of FIG. 5, for its part, illustrates that the second rod end 19 is indirectly secured to the upper yoke 10 via a second ball joint 42.
    According to the embodiment of the double-acting pressure reducing cylinder 1 according to the invention illustrated in FIGS. 1 to 5, the second rod end 19 of the traction rod 17 comprises a rod head 28 which holds the cylinder drum 71, the lower yoke 9 and the upper yoke 10 compressed together between said head 28 and the hollow abutment 13. This is made possible in particular by means of fastening lugs 25 which comprise said barrel 71 and said yokes 9, 10, said lugs 25 having ear hole 24 traversed by the second rod end 19. The zones "B" and "C" of Figure 5 illustrate this provision particularly clearly.
    FIGS. 4 and 5 show that the first rod end 18 of the traction rod 17 terminates - according to this non-limiting embodiment - by a thread of rod 29 screwed into a tapping 27 formed in a ball joint 42 which takes support in the transmission case 8 and around which articulates said first end 18.
    Thus, the various ball joints 42 around which the four hollowed abutments 13 articulate 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.
    Note however that this arrangement can not operate without the lower centering means of the cylinder 20 and the upper centering means of the cylinder 21 which each leaves the barrel cylinder 71 free to move parallel to its longitudinal axis relative to the transmission housing 8, but prohibited said barrel 71 to move in the plane perpendicular to said axis, always with respect to said casing 8.
    According to the non-limiting embodiment of the double-acting expander cylinder 1 according to the invention illustrated in FIGS. 3 and 4, the centering and sealing plate 53 and the centering gantry 22 which are rigidly secured to the casing each of 8 and 8 respectively carries the lower centering means of the cylinder 20 and the upper centering means of the cylinder 21, said lower and upper means 20 each consisting of an elastic centering disc 63.
    The elastic centering disk 63 which constitutes the lower centering means of the cylinder 20 is particularly visible in FIG. 6 while that constituting the upper centering means of the cylinder 21 is particularly visible in FIG.
    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.
    To illustrate the operation of the resilient centering disks 63, consider that which constitutes the lower centering means of the cylinder 20 and whose representation is particularly clear in FIG.
    It is noted in said FIG. 6 that 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 FIG. 4.
    It is found that 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. To ensure a sealed contact between said pad 67 and said cone 66, 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.
    As can easily be deduced, 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. In addition, said contact provides a seal which prevents the pressurized gases contained in the lower hot gas chamber 11 from escaping from said chamber 11.
    When - mainly under the effect of the temperature difference - the increase in the size of the assembly consisting of the cylinder drum 71, the lower yoke 9 and the upper yoke 10 is greater than that of the the assembly comprising the transmission casing 8, the centering gantry 22 and the rigid gantry pillar 23, the pressure exerted by the centering and sealing cone 66 of the lower yoke 9 on the male contact pad 67 increases this which deforms a little more axially and from its center the elastic centering disk 63.
    Since the dimensional differences in question relate only to tenths of a millimeter, the axial deformation of the centering elastic disk 63 does not compromise the integrity of the latter, which deforms in its elastic range. In addition, 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.
    Note in Figure 7 that the elastic centering disc 63 secured to the centering gantry 22 is provided to operate in a similar manner.
    Thus, 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.
    FIG. 6 shows the shaft sealing means 55 which seal between the lower hot gas chamber 11 and the lower piston rod 46 while ensuring the lubrication of the upper shaft seal 56 and the lower sealing rod 57 which constitute said means 55.
    It will be noted that 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.
    Still in FIG. 6, it is noted that, advantageously, the upper shaft seal 56 consists of two superimposed section segments whose sections are angularly offset while the lower shaft seal 57 consists of a single segment with a section said two seals 56, 57 being kept at a distance from each other by a segment spacer spring 61 which includes orifices allowing the flow of coolant and lubricating oil to pass between the supply conduit of cooling-lubricating oil 59 and the cooling-lubricating oil outlet duct 60, via the oil circulation chamber 58.
    FIG. 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, A limiting example taken here to illustrate the operation of the double-acting pressure reducing cylinder 1 according to the invention opens into the pressure chamber 44 arranged in the centering gantry 22 and which we have seen in description that it can supply compressed air via a internal channel that comprises the upper piston rod 47 sealing means 48 such as a perforated continuous ring 49 air cushion housed in a segment groove arranged at the periphery of the piston double-acting expander 2.
    When the heat transfer engine-relaxation and regeneration taken here as an example of application stops, it is noted that 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.
    Besides allowing the free expansion of the rigid assembly consisting of the cylinder barrel 71, the lower yoke 9 and the upper yoke 10, 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. For this, the recessed pillars 13 are not only of great length as illustrated in Figures 1 to 5, but they are also preferably made of a low thermal conductivity material such as zirconium oxide.
    In FIG. 5, it will be noted that to authorize the use of a steel pull rod 17 which requires staying at a low temperature, each pillar comprises a rod cooling tube 30 which tightly envelops said pull rod 17 with which it cooperates, over most 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 while the largest possible part 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.
    It will be noted in zone "A" of FIG. 5 that the shaft cooling tube 30 comprises a tube bulge 35 which ensures that said tube 30 remains locally centered in the rod tunnel 14. In addition, it is 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. These two other bulges 35 cooperate with a tube diameter restriction. 36 which carries out locally a seal between the rod cooling tube 30 and the pull rod 17.
    It will be noted in FIG. 4 that the shaft cooling tube 30 comprises a first tube supply port 32 located between said two other bulges 35, said first orifice 32 communicating with the inside of the stem cooling tube 30 in the vicinity the first rod end 18 on the one hand, and being connected to the forward circuit of the coolant source 40 via channels formed in the transmission case 8 on the other hand.
    In FIGS. 4 and 5 in zone "A", it is noted that the stem cooling tube 30 terminates - at the second rod end 19 - by a tube flange 34 held tight by the rod head 28 against a heat insulating riser 68 interposed between said flange 34 and the attachment lug 25 of the upper yoke 10. It will also be noted that a Banjo connector 38 is interposed between the rod head 28 and said flange 34, said coupling 38 having 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 rod cooling tube 30 on the other hand via the end of the cooling tube rod 30 which receives the tube collar 34.
    It is understood that the 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 .
    In any case, 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.
    In FIGS. 6 and 7, the relatively large radial length left on the elastic centering disc 63 between its disc fixing flange 65 and its contact pad 67 will be noted. If this length is necessary for said disc 63 to be deformable axially from its center, it is also useful to limit as much as possible the heat transfer from the centering and sealing cone 66 to said flange 65. As such, the body of the centering elastic disk 63 is preferably thin and made of zirconium oxide, known for its low thermal conductivity. It will also be noted that the low-width linear contact made between the centering and sealing cone 66 and the contact pad 67 also constitutes in itself an advantageous thermal barrier.
    The possibilities of the double-acting regulator cylinder 1 according to the invention are not limited to the applications just described and it must also be understood that the foregoing description has been given only as a example and that it does not limit in any way the field of said invention which one would not go out by replacing the execution details described by any other equivalent.
    权利要求:
    Claims (19)
    [1" id="c-fr-0001]
    An adaptive support double acting pressure reducing cylinder (1) comprising a cylinder barrel (71) cooperating with a double acting expansion piston (2) which is connected by a piston lower rod (46) to transmission means ( 3) housed in a transmission casing (8) on which is fixed the cylinder barrel (71), while the end of said barrel (71) which opens on the side of said means (3) is closed by a lower yoke (9). ) traversed by the lower piston rod (46) via a lower stem 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), characterized in that it comprises: • At least one hollow pillar (13) traversed from side to part in the direction of its length by a rod tunnel (14), a first pillar end (15) of said pillar (13) resting directly or indirectly on the transmission casing (8) while a second pillar end (16) of said pillar (13) directly or indirectly supports the cylinder barrel (71). ), the lower yoke (9) and the upper yoke (10), while said first end (15) can pivot about a ball joint (42) and / or bend relative to said casing (8) while said second end (15) end (16) is pivotable about a ball joint (42) and / or bent with respect to said barrel (71); At least one pull rod (17) housed in the rod tunnel (14), a first rod end (18) of said pull rod (17) being directly or indirectly secured to the transmission casing (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 about a ball joint (42) and / or bending with respect to said housing (8) while said second end (19) is pivotable about a ball joint (42) and / or flexing relative to cylinder (1); • Bottom centering means of the cylinder (20) positioned in the vicinity of the lower yoke (9), said means (20) being supported on the cylinder drum (71) or the lower yoke (9) of the first part, and directly or indirectly on the transmission casing (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 casing (8), but prohibiting said auditing barrel (71) to move in the plane perpendicular to said axis, always with respect to said casing (8); • Upper centering means of 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, and on a centering gantry (22) rigidly fixed to the transmission casing (8) and maintained at a height close to that of the upper yoke (10) by at least one rigid gantry pillar (23) of the second part, said means (21 ) leaving the cylinder barrel (71) free to move parallel to its longitudinal axis with respect to the transmission casing (8), but preventing said barrel (71) from moving in the plane perpendicular to said axis, always with respect to said casing (8).
    [2" id="c-fr-0002]
    2. double-acting pressure reducing cylinder according to claim 1, characterized in that it comprises at least one rod cooling tube (30) which sealingly envelops the pull rod (17) over all or part of the length of the said rod (17), a cooling fluid (31) from a source of cooling fluid (40) circulating in a space left between the inner wall of said tube (30) and the outer surface of said rod (17) however, 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.
    [3" id="c-fr-0003]
    3. double-acting pressure reducing cylinder according to claim 2, characterized in that it comprises at least a first tube supply port (32) communicating with the inside of the rod cooling tube (30) in the vicinity of the first stem end (18), and / or at least one second tube supply port (33) communicating with the interior of the stem cooling tube (30) in the vicinity of the second rod end (19), the cooling fluid (31) being able to circulate between the two said orifices (32, 33).
    [4" id="c-fr-0004]
    4. double-acting pressure reducing cylinder according to claim 2, characterized in that the rod cooling tube (30) comprises a tube flange (34) held directly or indirectly clamped by the pull rod (17) against one ear mounting (25) that has the cylinder drum (71) or the upper yoke (10), or against the transmission housing (8).
    [5" id="c-fr-0005]
    Double-acting pressure reducing cylinder according to Claim 4, characterized in that the tube flange (34) is held tight by the pull rod (17) against the fastening lug (25) via a Banjo connector (38) having at least one radial connection duct (39) connected to the cooling fluid source (40) on the one hand, and communicating with the interior of the rod cooling tube (30). somewhere else.
    [6" id="c-fr-0006]
    6. double-acting pressure reducing cylinder according to claim 4, characterized in that a thermal insulation riser (68) is interposed between the tube flange (34) and the attachment lug (25), said extension (68). ) being traversed throughout its length by a tunnel extension (69) in which is housed the pull rod (17) and the rod cooling tube (30) which tightly surrounds it that the largest possible part of the outer surface of said tube (30) does not touch the inner wall of the riser tunnel (69) so as to define with the latter wall a void space.
    [7" id="c-fr-0007]
    7. double-acting pressure reducing cylinder according to claim 2, characterized in that the rod cooling tube (30) comprises at least one tube bulge (35) consisting of an axial portion of said tube (30) whose diameter is substantially equivalent or slightly greater than that of the rod tunnel (14) in which it is housed.
    [8" id="c-fr-0008]
    8. double-acting pressure reducing cylinder according to claim 2, characterized in that the rod cooling tube (30) comprises at least one tube diameter restriction (36) consisting of an axial portion of said tube (30) whose diameter is substantially equivalent or slightly less than that of the body of the pull rod (17).
    [9" id="c-fr-0009]
    9. double-acting pressure reducing cylinder according to claim 2, characterized in that the rod cooling tube (30) comprises at least one radial communication hole (37) which allows the cooling fluid (31) to penetrate into said tube (30), or to escape.
    [10" id="c-fr-0010]
    10. double-acting pressure reducing cylinder according to claim 1, characterized in that the pull rod (17) is 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.
    [11" id="c-fr-0011]
    11. double-acting pressure reducing cylinder according to claim 1, characterized in that a pressure chamber (44) connected to a source of pressurized air (45) is fixed on the centering gantry (22) or arranged on or in the latter while an upper piston rod (47) which extends the double-acting expansion piston (2) on the side of the upper hot gas chamber (12) passes through the upper yoke (10) via a stem orifice upper (43) arranged in said cylinder head (10) and via a chamber access port (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) regardless of the position of said piston (2).
    [12" id="c-fr-0012]
    12. double-acting pressure reducing cylinder according to claim 1, characterized in that the transmission housing (8) is capped with a centering and sealing plate (53) pierced with an access orifice to the transmission means. (54) through which passes the lower piston rod (46) to be connected to the transmission means (3), said plate (53) being rigidly fixed on said housing (8).
    [13" id="c-fr-0013]
    A double-acting pressure reducing cylinder according to claim 11, characterized in that the chamber access port (52) cooperates with or includes rod sealing means (55) which seal between said orifice (52) and the upper piston rod (47).
    [14" id="c-fr-0014]
    14. double-acting pressure reducing cylinder according to claim 12, characterized in that the access opening to the transmission means (54) cooperates with or comprises rod sealing means (55) which provide a seal between said orifice (54) and the lower piston rod (46).
    [15" id="c-fr-0015]
    A double-acting pressure reducing cylinder according to claim 13 or 14, characterized in that the rod sealing means (55) comprise an upper stem seal (56) and a lower stem seal (57) sufficiently far apart. one of the other to form - between the two said seals (56, 57) - an oil circulation chamber (58) into which a cooling-lubricating oil supply duct (59) opens and from which relays a coolant-lubrication oil outlet conduit (60).
    [16" id="c-fr-0016]
    A double-acting pressure reducing cylinder according to claim 15, characterized in that the rod sealing means (55) cooperate with a rod guide ring (62) housed inside or outside the flow chamber. of oil (58).
    [17" id="c-fr-0017]
    17. Double acting pressure reducing cylinder according to claim 1, characterized in that the lower centering means of the cylinder (20) and / or the upper centering means of the cylinder (21) consist of an elastic centering disk (63). ) that can be drilled 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 disc fixing flange ( 65) respectively sealingly secured to the transmission casing (8) and / or the centering gantry (22).
    [18" id="c-fr-0018]
    18. Double-acting pressure reducing cylinder according to claim 12, characterized in that the centering and sealing plate (53) carries the lower centering means of the cylinder (20) which consist of an elastic centering disk (63). ) whose periphery forms a disc-fixing flange (65) sealingly attached to said platen (53), said disc (63) being pierced at its center with a disc-hole (64) through which the rod passes lower piston (46) without touching said disk (63), the edge of the disk hole (64) having a circular contact pad (67) which is kept in sealing contact with a centering and sealing cone (66) that the lower yoke (9) has, 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 elastic centering disc (63).
    [19" id="c-fr-0019]
    19. Double-acting pressure reducing cylinder according to claim 1, characterized in that the upper centering means of the cylinder (21) consist of a resilient centering disc (63) whose periphery forms a disc fixing flange (65). ) sealingly attached to the centering gantry (22), said disk (63) being pierced at its center with a disk hole (64) whose edge has a circular contact pad (67) which is kept in contact sealed with a centering cone and sealing (66) that has the upper yoke (10), said cone (66) being male or female, and the contact between said pad (67) and said cone (66) having the effect of axially deforming and from its center the centering elastic disc (63).
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    同族专利:
    公开号 | 公开日
    CN108138694A|2018-06-08|
    KR20180052657A|2018-05-18|
    CA2998581A1|2017-03-23|
    AU2016321973B2|2020-07-02|
    EP3350433B1|2019-08-07|
    ES2751760T3|2020-04-01|
    JP2018530697A|2018-10-18|
    FR3041040B1|2017-11-03|
    AU2016321973A1|2018-04-19|
    EP3350433A1|2018-07-25|
    JP6876035B2|2021-05-26|
    WO2017046479A1|2017-03-23|
    CN108138694B|2020-11-06|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3775973A|1970-05-04|1973-12-04|P Hudson|Combustion products pressure generators intermittent burner cycle and engines|
    US4307997A|1979-05-08|1981-12-29|The United States Of America As Represented By The United States Department Of Energy|Free piston inertia compressor|
    EP1306539A2|2001-10-24|2003-05-02|Enerlyt Potsdam GmbH|Two cycle hot gas engine|US10704431B2|2017-10-03|2020-07-07|Vianney Rabhi|Regenerative valve hydraulic actuator|IT1203452B|1987-04-07|1989-02-15|Tiziana Rigolli|INTERNAL COMBUSTION ROTARY ENGINE, WITH AXIAL PISTONS|
    US7137366B2|2004-09-10|2006-11-21|Tgs Innovations, Lp|Two-cycle swash plate internal combustion engine|
    CN102182582B|2011-03-22|2014-05-07|杨永顺|External combustion engine and transmission mechanism thereof|US11187184B2|2019-03-29|2021-11-30|Vianney Rabhi|Articulated plenum for transfer-expansion-regeneration combustion engine|
    FR3094416B1|2019-03-29|2021-03-05|Vianney Rabhi|ARTICULATED PLENUM|
    法律状态:
    2016-09-22| PLFP| Fee payment|Year of fee payment: 2 |
    2017-03-17| PLSC| Search report ready|Effective date: 20170317 |
    2017-09-18| PLFP| Fee payment|Year of fee payment: 3 |
    2018-09-25| PLFP| Fee payment|Year of fee payment: 4 |
    2019-09-25| PLFP| Fee payment|Year of fee payment: 5 |
    2020-09-25| PLFP| Fee payment|Year of fee payment: 6 |
    2021-09-27| PLFP| Fee payment|Year of fee payment: 7 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1558585A|FR3041040B1|2015-09-14|2015-09-14|DOUBLE EFFECT RETRACTOR CYLINDER WITH ADAPTIVE SUPPORT|FR1558585A| FR3041040B1|2015-09-14|2015-09-14|DOUBLE EFFECT RETRACTOR CYLINDER WITH ADAPTIVE SUPPORT|
    PCT/FR2016/052232| WO2017046479A1|2015-09-14|2016-09-07|Dual-acting expansion cylinder with adaptive support|
    JP2018513286A| JP6876035B2|2015-09-14|2016-09-07|Double acting decompression cylinder with compatible support|
    CN201680056803.6A| CN108138694B|2015-09-14|2016-09-07|Double-acting expansion cylinder with adaptive support|
    ES16775804T| ES2751760T3|2015-09-14|2016-09-07|Double acting decompressor cylinder with an adaptive mount|
    AU2016321973A| AU2016321973B2|2015-09-14|2016-09-07|Dual-acting expansion cylinder with adaptive support|
    KR1020187009338A| KR20180052657A|2015-09-14|2016-09-07|Double acting pressure reducing cylinder with adaptive support|
    CA2998581A| CA2998581A1|2015-09-14|2016-09-07|Dual-acting expansion cylinder with adaptive support|
    EP16775804.4A| EP3350433B1|2015-09-14|2016-09-07|Dual-acting expansion cylinder with adaptive support|
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