EP3143288B1 - Druckübersetzer mit kolben umfassend einen druckminderer in der endlage - Google Patents

Druckübersetzer mit kolben umfassend einen druckminderer in der endlage Download PDF

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Publication number
EP3143288B1
EP3143288B1 EP15732299.1A EP15732299A EP3143288B1 EP 3143288 B1 EP3143288 B1 EP 3143288B1 EP 15732299 A EP15732299 A EP 15732299A EP 3143288 B1 EP3143288 B1 EP 3143288B1
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European Patent Office
Prior art keywords
pressure
reducer
piston
slave
master
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EP15732299.1A
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English (en)
French (fr)
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EP3143288A1 (de
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Vianney Rabhi
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Individual
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
    • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
    • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
    • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring
    • F04B9/1076—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring with fluid-actuated inlet or outlet valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/17—Characterised by the construction of the motor unit of the straight-cylinder type of differential-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids

Definitions

  • the present invention relates to a piston pressure converter.
  • the amplifiers or piston pressure reducers generally consist of at least one emitter cylinder in which an emitting piston rigidly connected to at least one receiving piston can move, which can move in a receiving cylinder, the two said pistons moving on the piston. same race but with a different section.
  • Each said piston cooperates with a cylinder and a cylinder head to form a closed and sealed space of variable volume.
  • the emitter cylinder communicates with a hydraulic circuit independent of that of the receiver cylinder.
  • Piston amplifiers or pressure reducers can be used statically to maintain two circuits or two volumes independent of one another at a constant pressure ratio without necessarily establishing a flow of hydraulic fluid which involves the displacement of the emitter piston and the receiver piston.
  • the emitter piston is a hydraulic motor that converts a flow of hydraulic fluid in motion, said movement being communicated to the receiving piston which forms a hydraulic pump so as to transform said movement into a flow of fluid hydraulic.
  • the emitter piston must be larger than the receiving piston, while to reduce the pressure, the emitter piston must have a smaller section than the receiver piston.
  • the emitter cylinder comprises at least one inlet and at least one outlet which can each be held open or closed by a valve while the receiving cylinder has at least one inlet which comprises a non-return valve allowing the fluid hydraulic to enter said cylinder but not out, and at least one outlet which has a check valve allowing the hydraulic fluid out of said cylinder but not to enter.
  • the emitter piston when the emitter piston reaches the end of the stroke, the emitter cylinder is decompressed in a low pressure circuit without any counterpart in production of work, and the compression energy stored in the fluid Hydraulic is dissipated in the form of heat, Depending on the application considered, this loss makes it irrelevant the use of reducers or pressure amplifiers. In this respect, it would be particularly advantageous to be able to recover this compression energy, particularly with regard to piston pressure amplifiers or reducers operating at very high pressures.
  • the reversible hydraulic pressure converter with tubular valves object of the patent application WO2015025094-A1 included in the state of the art under Art.
  • the end-of-stroke expansion valve comprises an expansion receiver intake duct connected via the expansion receiver intake valve to the expansion receiver chamber cooperating with the variable volume expansion emitter chamber which communicates with the receiving chamber which is connected to the receiver intake duct while the detent receiver discharge duct connected to the same said detent receiving chamber is connected to the receiver discharge duct.
  • the end-of-stroke expansion valve comprises an expansion receiver intake duct connected via the expansion receiver intake valve to the expansion receiver chamber cooperating with the variable volume expansion emitter chamber which communicates with the emitter chamber which is connected to the emitter discharge duct while the expansion receiver discharge duct connected to the same said expansion receiver chamber is connected - upstream of the emitter intake valve - to the duct transmitter admission.
  • the end-of-stroke regulator comprises a progressive-action lever transmission which comprises a return spring of the expansion pistons which tends to keep the engine-emitter piston relaxing in the vicinity of its position where the trigger-emitting chamber has the smallest volume while simultaneously, said spring allows to maintain the pump piston-trigger receiver in the vicinity of its position where the expansion receiver chamber has the largest volume.
  • the end-of-stroke regulator comprises a progressive-action lever transmission which consists of a crank shaft rotatable in a crankshaft bearing and having a trigger-emitting piston crank with the crank pin of a crank is connected to a piston-engine piston-trigger shaft arranged in the engine-emitter piston relaxation by a piston rod trigger relaxation whose first end is articulated around said crankpin and whose second end is articulated about said axis, the crank shaft cooperating with secondary detent transmission means which mechanically connect said shaft with the pump piston-trigger receiver.
  • the limit expansion valve according to the present invention comprises secondary trigger transmission means which consist of an expansion gear toothed wheel which is integral in rotation with the crank shaft and which, when rotating, drives in translation. a linear expansion gear rack connected to the piston pump-trigger receiver.
  • the limit expansion valve according to the present invention comprises secondary triggering transmission means which consist of a piston-receiver crank integral in rotation with the crank shaft and whose crank pin is connected to an axis.
  • piston piston-receiver relaxation arranged in the piston pump-trigger receiver by a piston rod relaxation receiver whose first end is articulated around said crankpin and whose second end is articulated said axis.
  • the limit expansion valve according to the present invention comprises a progressive-action lever transmission which is constituted by a camshaft rotatable in a camshaft bearing and having a trigger-emitting piston cam which can be held in position. contact with the engine-emitter piston and a detent reciprocating piston cam that can be held in contact with the pump-receiver piston.
  • the end-of-stroke regulator comprises a crank shaft or a trigger-emitting piston crank or a trigger-emitting piston rod or a rebound-transmitting gear wheel or a rebound-transmitting gear rack or crank arm.
  • FIG. 1 to 8 the end-of-stroke regulator 1 for a piston-pressure converter 2 which comprises at least one emitter cylinder 3 in which a motor-emitter piston 7 can be displaced so as to define a transmitting chamber 9 of variable volume that can be put in relation with an emitter intake duct 22 by an emitter admission valve 18 or with an emitter discharge duct 23 by an emitter discharge valve 19 , said pressure converter 2 also comprising at least one receiving cylinder 4 in which a pump-receiver piston 8 can move so as to define a receiving chamber 10 also of variable volume, the latter being able to admit a hydraulic fluid coming from a Receiver inlet conduit 24 via a receiver inlet valve 20 or discharge said fluid into a receiver discharge conduit 25 via a receiver discharge valve 21, the emitter chamber 9 and the receiving chamber 10 being each filled with a hydraulic fluid.
  • the end-of-stroke regulator 1 comprises at least one trigger-emitting cylinder 12, filled with a hydraulic fluid, and in which a motor-emitter-expansion piston 14 can be displaced so as to define an emitting chamber detent 16 of variable volume which communicates with the receiving chamber 10.
  • the end-of-stroke expander 1 comprises at least one expansion emitter cylinder 12, filled with a hydraulic fluid, and in which a motor piston can be moved.
  • trigger transmitter 14 so as to define an expansion emitter chamber 16 of variable volume which communicates with the emitter chamber 9.
  • the expansion emitter chamber 16 can communicate - as the case may be - either with the emitter chamber 9 or with the receiving chamber 10 via a duct arranged in a cylinder head relaxation transmitter 44 on the emitting cylinder 12, or simply because the expansion emitter cylinder 12 opens directly into either the emitter chamber 9 or the receiving chamber 10.
  • said emitter cylinder 12 does not have an expansion emitter cylinder head 44 and can respectively to terminate at the inner surface of a cylinder cylinder head 5 capping the emitter cylinder 3 or at the inner surface of a receiver cylinder head 6 capping the receiver cylinder 4.
  • the end-of-stroke regulator 1 comprises at least one rebound-receiving cylinder 13 which cooperates with the expansion-emitter cylinder 12 and in which a pump-receiver-expansion piston 15 can be displaced so as to define with said the receiver cylinder 13 has a variable volume expansion chamber 17 filled with a hydraulic fluid, said pump-receiver piston 15 being mechanically connected to the engine-emitter piston 14 by a progressive lever gear lever 11 arranged in such a way that when the engine-emitter piston 14 is at the top dead center, the piston-receiver piston relaxation is at low dead center and vice versa, while the maximum volume of the expansion receiver chamber 17 is less than the maximum volume of the relaxing emitting chamber 16.
  • the progressive lever transmission 11 defines between the engine-emitter piston 14 and the pump-receiver piston 15 a transmission ratio such that when said engine-emitter piston 14 is placed in its neutral position high and as a result the volume of the expansion emitting chamber 16 is minimal, said engine-emitter piston 14 can not - despite the pressure of the hydraulic fluid to which it is exposed - move and thereby cause the piston-receiver piston 15, while the more the engine-emitter piston relaxation 14 is removed from said top dead center, the greater the effort it is able to transmit to the piston pump-trigger receiver 15 is important, as well as its capacity to move said pump-receiver piston 15. It is further noted that the engine-emitter piston relaxation 14 and / or the pump piston-receiver receiver 15 may comprise at least one seal and / or at least one segment of seal Eite.
  • the Figures 1 to 8 show that the end-of-stroke regulator 1 according to the invention comprises at least one expansion receiver intake valve 26 which opens into the expansion receiving chamber 17 and which allows a hydraulic fluid contained in an intake duct of relaxation receiver 28 to enter said receiving chamber 17 but not out.
  • the Figures 1 to 8 also show that the end-of-stroke regulator 1 comprises at least one expansion receiver discharge valve 27 which opens into the expansion receiver chamber 17 and which allows a fluid hydraulic fluid contained in an expansion receiver discharge duct 29 out of said receiving chamber 17 but not to enter.
  • expansion receiver intake valve 26 and / or the expansion receiver discharge valve 27 can be arranged in a relaxation receiver cylinder head 45 which closes off one end of the expansion receiver cylinder. 13 or in the closed end of said cylinder 13 if it is blind.
  • the end-of-stroke regulator 1 also comprises at least one trigger release actuator 30 which can, by contact or mechanical connection, set the progressive-action lever transmission 11 in motion or unblock the latter so as to set in motion the engine-emitter piston relaxation 14 and the piston pump-trigger receiver 15 when the piston engine-emitter relaxation 14 is placed in its top dead center or in the vicinity of the latter, and this for example to achieve a report transmission between said pistons 14, 15 sufficient for the engine-emitter piston relaxation 14 can continue its course without the aid of the trigger release actuator 30.
  • trigger release actuator 30 can, by contact or mechanical connection, set the progressive-action lever transmission 11 in motion or unblock the latter so as to set in motion the engine-emitter piston relaxation 14 and the piston pump-trigger receiver 15 when the piston engine-emitter relaxation 14 is placed in its top dead center or in the vicinity of the latter, and this for example to achieve a report transmission between said pistons 14, 15 sufficient for the engine-emitter piston relaxation 14 can continue its course without the aid of the trigger release actuator 30.
  • the trigger release actuator 30 can be hydraulic, electro-hydraulic, electric, pneumatic, or generally, of any type known to those skilled in the art.
  • the trigger release actuator 30 can be controlled by a control computer 55 of the pressure converter which manages or cooperates to manage the operation of the piston pressure converter 2.
  • the expansion receiver intake duct 28 connected via the expansion receiver intake valve 26 to the expansion receiver chamber 17 cooperating with the variable volume expansion chamber 16 which communicates with the receiving chamber 10 may be connected to the receiver intake duct 24 while the expansion receiver discharge duct 29 connected to the same said expansion receiver chamber 17 can be connected to the receiver discharge duct 25.
  • the expansion receiver intake duct 28 connected via the expansion receiver intake valve 26 the relaxation receiving chamber 17 cooperating with the expansion emitter chamber 16 of variable volume which communicates with the emitter chamber 9 can be connected to the emitter discharge conduit 23 while the expansion receiver discharge conduit 29 connected to the even said relaxation receiving chamber 17 may be connected - upstream of the emitter admission valve 18 - to the emitter intake duct 22.
  • the progressive lever transmission 11 may comprise a return spring for the expansion pistons 33 which tends to keep the engine-emitter piston 14 relaxing in the vicinity of its position where the trigger-emitting chamber 16 presents the most while simultaneously, said spring 33 makes it possible to maintain the pump-receiver piston 15 relaxing in the vicinity of its position where the expansion receiving chamber 17 has the largest volume, said spring 33 being able to be torsion, flexion, traction or compression and be of any type known to those skilled in the art.
  • the progressive-action lever transmission 11 may consist of a crank shaft 46 which can rotate in a crankshaft bearing 47 and having a piston crank trigger transmitter 35 whose crank pin 48 is connected to a piston-engine piston axis relaxation 49 arranged in the piston engine-trigger 14 by a piston rod relaxation transmitter 34 whose first end is articulated around said crank pin 48 and whose second end is hinged about said axis 49, the crank shaft 46 cooperating with secondary expansion means of transmission 51 which mechanically connect said shaft 46 with the pump-receiver piston relaxation 15.
  • the secondary transmission means of relaxation 51 may consist of a gear transmission gear 34 which is integral in rotation with the crank shaft 46 and that when rotated in linear translation drives a transmission rack the trigger 37 is connected to the pump-receiver piston 15 directly or by means of a trigger rest piston push rod 39.
  • the trigger transmission rack 37 can be guided, in particular by at least one trigger rack guide roller 38.
  • the secondary triggering transmission means 51 may consist of a trigger-receiving piston crank 40 integral in rotation with the crankshaft 46 and whose crank pin 48 is connected to a pump-receiver piston pin of trigger 50 arranged in the pump piston-receiver relaxation 15 by a piston rod relaxation receiver 41 whose first end is articulated around said crankpin 48 and whose second end is hinged about said axis 50.
  • the secondary transmission means of relaxation 51 may also consist of a cam integral in rotation with the crank shaft 46 and can be kept in contact with the pump-receiver piston relaxing 15.
  • the progressive-action lever transmission 11 may be constituted by a camshaft 52 rotatable in a camshaft bearing 53 and having a detent-emitting piston cam 42 which can be held in contact with the engine piston.
  • trigger transmitter 14 and an expansion receiver piston cam 43 which can be kept in contact with the pump-receiver piston 15.
  • the detent reciprocating piston cam 43 can be replaced by a crank integral in rotation with the camshaft 52, said crank having a crankpin connected to an axis arranged in the piston pump-trigger receiver 15 by a connecting rod whose first end is articulated around said crankpin and whose second end is articulated about said axis.
  • crankshaft 46 or the trigger-emitting piston crank 35 or the trigger-emitting piston rod 34 or the rebound-transmitting gear 36 or the rebound-transmitting gear 37 or the receiver piston crank detent 40 or the trigger piston piston rod 41 or the camshaft 52 or the trigger emitter piston cam 42 or the expansion receiver piston cam 43 may have a detent release push-button 32 on which the trigger release actuator 30 can exert a force via a release release button 31 to put in motion at the appropriate moment the piston engine-transmitter relaxation 14 and the piston pump-trigger receiver 15 when the piston engine-emitter relaxation 14 is placed in its top dead center or in the vicinity of the latter.
  • Figures 1 to 8 show a variant according to which the trigger release push-button 32 is provided on the trigger-emitting piston crank 35.
  • the application illustrated by the figure 1 is intended to convert stored energy in the form of compressed nitrogen into a high-pressure fluid reservoir 58 into electricity by means of an electricity generator 62 driven by a medium-pressure hydraulic motor 59. Nitrogen compressed communicates its pressure to a hydraulic fluid that can circulate in particular in the ducts 64.
  • a piston pressure converter 2 has thus been inserted between the high-pressure fluid reservoir 58 and the medium-pressure hydraulic motor 59 which converts a high-pressure flow of hydraulic fluid coming out of said reservoir 58 into a medium-pressure flow rate of hydraulic fluid, the latter entering the medium-pressure hydraulic motor 59 via an inlet duct of the hydraulic motor 60.
  • the inlet duct of the hydraulic motor 60 comprises - according to this example - a medium-pressure fluid reservoir 57.
  • the management computer of the converter pressure 55 opens the emitter intake valve 18 which allows the hydraulic fluid contained in the high-pressure fluid reservoir 58 to enter the emitter chamber 9 via the emitter intake duct 22.
  • said calculator 55 simultaneously prevents said fluid from leaving said chamber 9 to go to the emitter outlet low-pressure fluid reservoir 56, said computer 55 maintaining for this the emitter discharge valve 19 closed.
  • the hydraulic fluid under high pressure from said reservoir 58 can push on the engine-emitter piston 7, which moves in the direction d2 , which has the effect of moving the pump-receiver piston 8 in the same direction, on the same distance and at the same speed.
  • the pump-receiver piston 8 compresses the hydraulic fluid contained in the receiving chamber 10, which has the effect of expelling said fluid in the receiver discharge pipe 25 via the receiver discharge valve 21. Said fluid is then conveyed via a duct 64 to the inlet duct of the hydraulic motor 60, which has the effect of rotating the medium-pressure hydraulic motor 59 and consequently the electricity generator 62, which produces electricity.
  • the position sensor of the pressure converter pistons 54 continuously returns the position of the pump-receiver piston 8 to the control computer of the pressure converter 55.
  • said computer 55 closes the emitter admission valve 18 so as to stop the displacement of the pump-receiver piston 8 in the direction d2 before it touches said cylinder head 6, and so that said piston 8 remains at a certain distance from the said cylinder head 6.
  • the management computer of the pressure converter 55 should at this stage open the emitter discharge valve 19 to decompress said chamber 9 in the emitter outlet low-pressure fluid reservoir 56, this which would have the effect of dissipating the compression energy of the hydraulic fluid contained in the emitter chamber 9, said energy being definitively no longer able to be transformed into additional flow of hydraulic fluid leaving the receiver discharge pipe 25.
  • the end-of-stroke pressure regulator 1 for a piston pressure converter 2 provides that the control computer of the pressure converter 55 does not open the valve yet. emitter discharge 19 so that said expander 1 can produce its effects and recover the compression energy of the hydraulic fluid contained in the emitter chamber 9.
  • the management computer of the pressure converter 55 supplies the trigger release actuator 30 with electric current, which has the effect of setting the transmission in motion. with progressive effect lever 11 and consequently, to set in motion the piston engine-emitter relaxation 14 and the pump piston-receiver of relaxation 15, the piston engine-emitter relaxation 14 being hitherto parked in its top dead center .
  • the figure 3 shows the state in which the end-of-stroke regulator 1 according to the invention was located as long as the engine-emitter piston 7 and the pump-receiver piston 8 were moving in the direction d2 . It should be noted that the engine-emitter piston 14 remains stuck in its top dead center because the pressure that the hydraulic fluid contained in the receiving chamber 10 exerted on said piston 14 tended to turn the crank shaft 46 in the opposite direction of the Clockwise.
  • the piston motor-emitter relaxation 14 remains blocked is due to the fact that - according to this particular embodiment illustrated in figure 3 and 4 when said piston is parked at its top dead center, the axis of rotation of the crank pin 48 is substantially misaligned with respect to the straight line which connects the axis of rotation of the engine-emitter piston pin 49 and the axis of rotation of the crankshaft 46, while the center of rotation of the piston-motor piston axis relaxation 49 and the axis of the cylinder emitter of 12 are perpendicular and intersecting, and that is the same for the axis of rotation of the crank shaft 46 and said axis of said cylinder 12.
  • the engine-emitter piston 7 and the piston pump-receiver 8 are temporarily stopped.
  • the pressure in the emitting chamber 9 approximately corresponds to the pressure in the high-pressure fluid reservoir 58 while the pressure prevailing in the receiving chamber 10 is equivalent to the pressure that previously prevailed in the inlet duct of the hydraulic motor 60.
  • the transmission ratio between the piston engine-emitter relaxation 14 and the piston pump-recess receiver 15 is large or infinitely large when said engine-emitter piston 14 is placed on or near from its top dead center, and small when said engine-emitter piston 14 is positioned at the bottom dead center. It is also noted that advantageously, the complete stroke of the engine piston-emitter relaxation 14 operates only a quarter turn of the crank shaft 46.
  • This decreasing transmission ratio derives - firstly - from the system constituted by the push-back piston connecting rod 34 and the trigger-emitting piston crank 35, said system offering a short or even infinitely short lever arm to the engine-emitter piston 14 to rotate the crank shaft 46 when said piston 14 is on or near its top dead center, said lever arm becoming maximum when said piston 14 is in its bottom dead center.
  • This decreasing transmission ratio comes from the second part because, unlike the piston motor-emitter trigger 14, the linear translation drive of the piston pump-trigger receiver 15 by the shaft to crank 46 operates at constant leverage since the secondary drive means of relaxation 51 in question are constituted - according to this non-limiting embodiment - of a toothed gear transmission of trigger 36 driving a push-and-turn gear rack 37 .
  • the difference in section and the variable transmission ratio between the engine-emitter piston 14 and relaxation piston-receiver piston 15 can relax the hydraulic fluid contained in the emitter chamber 9 and the receiving chamber 10 in the desired conditions c That is, using this trigger to generate a medium-pressure hydraulic fluid flow adds up! available at the inlet duct of the hydraulic motor 60.
  • the pressure in the receiving chamber 10 is substantially equal to the desired pressure at the duct hydraulic motor input 60.
  • the force exerted by the pressure in the receiving chamber 10 on the engine piston-emitter 14 is - for example - ten times greater than that which must be exerted on the pump piston-receiver for the latter to produce the desired pressure in the expansion receiver chamber 17.
  • the instantaneous transmission ratio between the engine-emitter piston relaxation 14 and the piston pump-trigger receiver 15 is - for example - of one out of ten.
  • the pump piston-receiver piston 15 well pressurizes the expansion receiver chamber 17 with which it cooperates with the desired pressure, so that it begins to expel from said receiving chamber 17 the hydraulic fluid that it contains in the expansion receiver discharge duct 29 via the expansion receiver discharge valve 27.
  • the engine-emitter piston 7 and the pump-receiver piston 8 begin to advance substantially in the direction d2 under the effect of the expansion of the emitter chamber 9.
  • the operating piston-emitter piston 14 moves towards its bottom dead point while decreases the pressure it receives from the hydraulic fluid coming from the receiving chamber 10. In doing so, the transmission ratio between said piston 14 and the The pump-recess piston 15 increases to approximately one when the piston engine-trigger 14 reaches its bottom dead center.
  • the management computer of the pressure converter 55 can open the emitter discharge valve 19.
  • the engine-emitter piston 7 and the pump-receiver piston 8 move rapidly in the direction d1 under the effect of the pressure exerted by the hydraulic fluid contained in the low-pressure receptor inlet fluid reservoir 63 on the entire section of the pump-receiver piston 8, via the valve d Receiver intake 20.
  • the control computer of the pressure converter 55 closes the emitter discharge valve 19 and the engine-emitter piston 7 and the pump-receiver piston 8 stops moving in the direction d1 .
  • the return spring of the expansion pistons 33 brings the engine-emitter piston trigger 14 to the top dead center, and brings the push-release trigger push-button 32 into contact with the trigger release button 31.
  • the piston pump-trigger receiver 15 returns to its bottom dead center by sucking - via the expansion receiver intake valve 26 - hydraulic fluid from the low-pressure receiver inlet fluid reservoir 63 so as to fill the relaxation guest room 17.
  • the engine-emitter piston 7 and the pump-receiver piston 8 of the piston pressure converter 2 are ready to carry out a new stroke in the direction d2 to convert the high-pressure flow of hydraulic fluid leaving the reservoir high-pressure fluid 58 at a medium-pressure flow rate of hydraulic fluid entering the medium-pressure hydraulic motor 59 before exiting via the outlet duct of the hydraulic motor 61 to finally open into a hydraulic fluid cover 65.
  • end-of-stroke regulator 1 is again ready to decompress the emitting chamber 9 and to recover the compression energy of the hydraulic fluid contained in said chamber 9 when the pump-receiver piston 8 again arrives. near the receiver cylinder head 6.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (9)

  1. Druckübersetzer mit Kolben (2), der wenigstens einen Geberzylinder (3) umfasst, in welchem sich ein Motor- und Geberkolben (7) bewegen kann, derart, dass eine Abgabekammer (9) mit variablem Volumen definiert wird, zu der durch ein Geber-Einlassventil (18) eine Verbindung mit einer Geber-Einlassleitung (22) oder durch ein Geber-Auslassventil (19) mit einer Geber-Auslassleitung (23) hergestellt werden kann, wobei der Druckübersetzer (2) außerdem wenigstens einen Nehmerzylinder (4) umfasst, in welchem sich ein Pumpen- und Nehmerkolben (8) bewegen kann, derart, dass eine Aufnahmekammer (10), ebenfalls mit variablem Volumen, definiert wird, wobei diese Letztere über ein Nehmer-Einlassklappenventil (20) ein von einer Nehmer-Einlassleitung (24) kommendes Hydraulikfluid einlassen oder dieses Fluid über ein Nehmer-Auslassklappenventil (21) in eine Nehmer-Auslassleitung (25) ausstoßen kann, wobei die Abgabekammer (9) und die Aufnahmekammer (10) jeweils mit einem Hydraulikfluid gefüllt sind, dadurch gekennzeichnet, dass der Druckübersetzer (2) außerdem einen Druckminderer in der Endlage (1) aufweist, welcher umfasst:
    • wenigstens einen Druckminder-Geberzylinder (12), der mit einem Hydraulikfluid gefüllt ist und in welchem sich ein Druckminder-Motor-und Geberkolben (14) bewegen kann, derart, dass eine Druckminder-Abgabekammer (16) mit variablem Volumen definiert wird, welche mit der Abgabekammer (9) und/oder mit wenigstens einem Druckminder-Geberzylinder (12) kommuniziert, der mit einem Hydraulikfluid gefüllt ist, und in welchem sich ein Druckminder-Motor- und Geberkolben (14) bewegen kann, derart, dass eine Druckminder-Abgabekammer (16) mit variablem Volumen definiert wird, welche mit der Aufnahmekammer (10) kommuniziert;
    • wenigstens einen Druckminder-Nehmerzylinder (13), welcher mit dem Druckminder-Geberzylinder (12) zusammenwirkt und in welchem sich ein Druckminder-Pumpen- und Nehmerkolben (15) bewegen kann, derart, dass mit dem Nehmerzylinder (13) eine Druckminder-Aufnahmekammer (17) mit variablem Volumen definiert wird, die mit einem Hydraulikfluid gefüllt ist, wobei der Pumpen- und Nehmerkolben (15) mit dem Druckminder-Motor- und Geberkolben (14) mechanisch durch eine progressiv wirkende Hebelübersetzung (11) verbunden ist, die derart beschaffen ist, dass, wenn sich der Druckminder-Motor- und Geberkolben (14) im oberen Totpunkt befindet, der Druckminder-Pumpen- und Nehmerkolben (15) sich im unteren Totpunkt befindet, und umgekehrt;
    • wenigstens ein Druckminder-Nehmer-Einlassklappenventil (26), welches in die Druckminder-Aufnahmekammer (17) mündet und welches einem Hydraulikfluid, das in einer Druckminder-Nehmer-Einlassleitung (28) enthalten ist, ermöglicht, in die Aufnahmekammer (17) einzuströmen, jedoch nicht, aus ihr auszuströmen;
    • wenigstens ein Druckminder-Nehmer-Auslassklappenventil (27), welches in die Druckminder-Aufnahmekammer (17) mündet und welches einem Hydraulikfluid, das in einer Druckminder-Nehmer-Auslassleitung (29) enthalten ist, ermöglicht, aus der Aufnahmekammer (17) auszuströmen, jedoch nicht, in sie einzuströmen;
    • wenigstens einen Druckminder-Freigabeaktuator (30), der durch Kontakt oder mechanische Verbindung die progressiv wirkende Hebelübersetzung (11) in Bewegung setzen oder diese Letztere freigeben kann.
  2. Druckübersetzer (2) nach Anspruch 1, dadurch gekennzeichnet, dass die Druckminder-Nehmer-Einlassleitung (28), die über das Druckminder-Nehmer-Einlassklappenventil (26) mit der Druckminder-Aufnahmekammer (17) verbunden ist, die mit der Druckminder-Abgabekammer (16) mit variablem Volumen zusammenwirkt, welche mit der Aufnahmekammer (10) kommuniziert, mit der Nehmer-Einlassleitung (24) verbunden ist, während die Druckminder-Nehmer-Auslassleitung (29), die mit derselben Druckminder-Aufnahmekammer (17) verbunden ist, mit der Nehmer-Auslassleitung (25) verbunden ist.
  3. Druckübersetzer (2) nach Anspruch 1, dadurch gekennzeichnet, dass die Druckminder-Nehmer-Einlassleitung (28), die über das Druckminder-Nehmer-Einlassklappenventil (26) mit der Druckminder-Aufnahmekammer (17) verbunden ist, die mit der Druckminder-Abgabekammer (16) mit variablem Volumen zusammenwirkt, welche mit der Abgabekammer (9) kommuniziert, mit der Geber-Auslassleitung (23) verbunden ist, während die Druckminder-Nehmer-Auslassleitung (29), die mit derselben Druckminder-Aufnahmekammer (17) verbunden ist, stromaufwärts des Geber-Einlassventils (18) mit der Geber-Einlassleitung (22) verbunden ist.
  4. Druckübersetzer (2) nach Anspruch 1, dadurch gekennzeichnet, dass die progressiv wirkende Hebelübersetzung (11) eine Rückholfeder (33) für die Druckminder-Kolben aufweist, welche bestrebt ist, den Druckminder-Motor-und Geberkolben (14) in der Nähe seiner Position zu halten, in der die Druckminder-Abgabekammer (16) das kleinste Volumen aufweist, während diese Feder (33) gleichzeitig ermöglich, den Druckminder-Pumpen- und Nehmerkolben (15) in der Nähe seiner Position zu halten, in der die Druckminder-Aufnahmekammer (17) das größte Volumen aufweist.
  5. Druckübersetzer (2) nach Anspruch 1, dadurch gekennzeichnet, dass die progressiv wirkende Hebelübersetzung (11) aus einer Kurbelwelle (46) besteht, die in einem Kurbelwellenlager (47) rotieren kann und eine Druckminder-Geberkolben-Kurbel (35) aufweist, deren Kurbelzapfen (48) mit einer in dem Druckminder-Motor- und Geberkolben (14) angeordneten Achse (49) des Druckminder-Motor- und Geberkolbens (14) durch eine Druckminder-Geberkolbenstange (34) verbunden ist, deren erstes Ende um den Zapfen (48) herum angelenkt ist und deren zweites Ende um die Achse (49) herum angelenkt ist, wobei die Kurbelwelle (46) mit sekundären Druckminder-Übersetzungsmitteln (51) zusammenwirkt, welche die Welle (46) mit dem Druckminder-Pumpen- und Nehmerkolben (15) mechanisch verbinden.
  6. Druckübersetzer (2) nach Anspruch 5, dadurch gekennzeichnet, dass die sekundären Druckminder-Übersetzungsmittel (51) aus einem Druckminder-Übersetzungszahnrad (36) bestehen, welches mit der Kurbelwelle (46) drehfest verbunden ist und welches, wenn es sich dreht, eine Druckminder-Übersetzungszahnstange (37) linear antreibt, die mit dem Druckminder-Pumpen- und Nehmerkolben (15) verbunden ist.
  7. Druckübersetzer (2) nach Anspruch 5, dadurch gekennzeichnet, dass die sekundären Druckminder-Übersetzungsmittel (51) aus einer Druckminder-Nehmerkolben-Kurbel (40) bestehen, die mit der Kurbelwelle (46) drehfest verbunden ist und deren Kurbelzapfen (48) mit einer in dem Druckminder-Pumpen- und Nehmerkolben (15) angeordneten Achse (50) des Druckminder-Pumpen- und Nehmerkolbens durch eine Druckminder-Nehmerkolbenstange (41) verbunden ist, deren erstes Ende um den Zapfen (48) herum angelenkt ist und deren zweites Ende um die Achse (50) herum angelenkt ist.
  8. Druckübersetzer (2) nach Anspruch 1, dadurch gekennzeichnet, dass die progressiv wirkende Hebelübersetzung (11) aus einer Nockenwelle (52) besteht, die in einem Nockenwellenlager (53) rotieren kann und einen Druckminder-Geberkolben-Nocken (42), der mit dem Druckminder-Motor-und Geberkolben (14) in Kontakt gehalten werden kann, und einen Druckminder-Nehmerkolben-Nocken (43), der mit dem Druckminder-Pumpen- und Nehmerkolben (15) in Kontakt gehalten werden kann, aufweist.
  9. Druckübersetzer (2) nach einem der Ansprüche 5 bis 8, dadurch gekennzeichnet, dass die Kurbelwelle (46) oder die Druckminder-Geberkolben-Kurbel (35) oder die Druckminder-Geberkolbenstange (34) oder das Druckminder-Übersetzungszahnrad (36) oder die Druckminder-Übersetzungszahnstange (37) oder die Druckminder-Nehmerkolben-Kurbel (40) oder die Druckminder-Nehmerkolbenstange (41) oder die Nockenwelle (52) oder der Druckminder-Geberkolben-Nocken (42) oder der Druckminder-Nehmerkolben-Nocken (43) einen Druckminder-Freigabedruckknopf (32) aufweist, auf welchen der Druckminder-Freigabeaktuator (30) über ein Druckminder-Freigabefolgeglied (31) eine Kraft ausüben kann.
EP15732299.1A 2014-05-12 2015-05-07 Druckübersetzer mit kolben umfassend einen druckminderer in der endlage Active EP3143288B1 (de)

Applications Claiming Priority (3)

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FR1454223A FR3020840B1 (fr) 2014-05-12 2014-05-12 Detendeur de fin de course pour convertisseur de pression a pistons
FR1455710A FR3020841B1 (fr) 2014-05-12 2014-06-20 Detenteur de fin de course pour convertisseur de pression a pistons
PCT/FR2015/051209 WO2015173495A1 (fr) 2014-05-12 2015-05-07 Détendeur de fin de course pour convertisseur de pression a pistons

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US9856891B2 (en) 2018-01-02
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CA2946466A1 (fr) 2015-11-19
KR102277604B1 (ko) 2021-07-14
KR20170002430A (ko) 2017-01-06
CN106662082A (zh) 2017-05-10
ES2709397T3 (es) 2019-04-16
FR3020840B1 (fr) 2017-03-03
CN106662082B (zh) 2018-12-28
JP2017520725A (ja) 2017-07-27
CA2946466C (fr) 2022-09-06
FR3020841A1 (fr) 2015-11-13
AU2015261366B2 (en) 2018-08-23
FR3020841B1 (fr) 2017-07-07
AU2015261366A1 (en) 2016-12-15
FR3020840A1 (fr) 2015-11-13
WO2015173495A1 (fr) 2015-11-19

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