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 an end-of-stroke regulator for a piston pressure converter.
• the amplifiers or piston pressure reducers generally consist of at least one emitter cylinder in which an emitter 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 each other in a constant pressure ratio without necessarily establishing a flow of hydraulic fluid which involves 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 the cylinder but not to enter.
• the reversible hydraulic pressure converter valves tubuiaires subject of the patent application 5 1358071 of August 20, 2013 owned by the applicant would see its significantly increased energy efficiency if it cooperated with recovery means (energy compression of the hydraulic fluid , regardless of the context of implementation of said converter.It is also noted that if said converter is used to produce hydraulic hybrid transmission vehicles with storage-restitution of oil under pressure, recover the compression energy of the hydraulic fluid in said converter becomes particularly advantageous and makes it possible to reduce the fuel consumption per kilometer of said vehicles, the energy advantage induced by means for recovering the compression energy of the hydraulic fluid would also benefit any converter, amplifier or reduction gear of pressure s quentiel piston, regardless of the number of pistons transmitter (s) or receptor (s) it contains, and regardless of its field of application.
• the limit expansion valve according to the invention provided for a piston pressure converter which comprises at least one emitter cylinder in which can move a motor-emitter piston so as to define an emitter chamber of variable volume that can be implemented.
• Each fluid filled with a hydraulic fluid comprises: At least one trigger-emitting cylinder, filled with a hydraulic fluid, and in which a piston-emitter piston can be displaced so as to define a volume-triggering emitter chamber variable which communicates with the emitter chamber and / or at least one expansion emitter cylinder, filled with a hydraulic fluid, and in which can move a piston engine-emitter relaxation so as to define a volume triggering emitter chamber variable that communicates with the receiving chamber;
• At least one expansion receiver cylinder which cooperates with the expansion emitter cylinder and in which can move a pump piston-trigger receiver so as to define with said receiving cylinder a variable volume expansion receiver chamber filled with a fluid hydraulic, said pump-receiver piston being mechanically connected to the piston motor-emitter trigger by a progressive lever transmission arranged so that when the piston engine-trigger is at the top dead center, the piston pump-trigger receiver is at the bottom dead center and vice versa, while the maximum volume of the relaxation chamber is less than the maximum volume of the relaxation chamber;
• At least one expansion receiver inlet valve which opens into the expansion receiver chamber and which allows a hydraulic fluid contained in an expansion receiver inlet duct to enter said receiving chamber but not into exit ;
• At least one expansion receiver discharge valve that opens into the expansion receiver chamber and allows a hydraulic fluid contained in a relief receiver discharge conduit to exit but not to enter the receiving chamber;
• At least one trigger release actuator can by contact or mechanical connection set in motion the progressive lever transmission or unlock the latter.
• the limit valve according to the present invention comprises a conduit relaxing receiver inlet connected via the valve to trigger receptor admission to the receiving expansion chamber cooperating with the donor chamber of variable volume communicating with relaxing 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 regulator comprises an expansion receiver inlet 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 admission of an issuer
• the end-of-stroke regulator according to the present invention 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 It has the smallest volume while simultaneously, said spring allows to maintain the pump-receiver piston relaxation in the vicinity of its position where the trigger-receiving 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 which is The crank is connected to a piston-engine piston-trigger shaft arranged in the engine-emitter piston relaxation by a relaxing trigger piston rod whose first end is articulated around said maniion 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 a trigger transmission gear 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 trigger 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 dudii crank pin and whose second end is articulated dudii 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 piston- trigger transmitter and a detent reciprocating piston cam which can be held coniBCt with the pump piston-trigger receiver.
• the following limit expansion device of the present invention comprises a crankshaft or a trigger-emitting piston crank or a trigger-emitting piston rod or a rebound-transmitting gear or a rebound-transmitting gear or a crank. of a recess piston or a relaxation piston piston or a camshaft or a trigger-emitting piston cam or a rebound-receiver piston cam which has a trigger-release push-stop on which the piston actuator Relaxation unlocking can exert effort through a relaxing release pad.
• Figure 1 schematically illustrates the end-of-stroke pressure regulator for piston pressure converter according to the present invention as it can be provided to cooperate with a single-chamber and a single receiver chamber piston pressure converter, said converter being implemented for converting a flow of high pressure hydraulic fluid from a high pressure fluid reservoir into a medium pressure hydraulic fluid flow, and this, to drive a medium pressure hydraulic motor coupled to a generator electricity.
• FIG. 2 schematically illustrates the end-of-travel regulator for a piston pressure converter according to the present invention, such that it can be provided for cooperating with a two-chamber emitter piston pressure converter and two receiver chambers. being used to convert a flow of high pressure hydraulic fluid from a high pressure fluid reservoir into a medium pressure hydraulic fluid flow, and this, to drive a medium pressure hydraulic motor coupled to a generator 'electricity.
• FIG. 3 and 4 are diagrammatic sections illustrating the operation of the end-of-stroke pressure regulator for a piston pressure converter according to the present invention and according to a variant in which the progressive-action lever transmission consists of a crank shaft comprising a crank trigger-emitting piston piston whose crank pin is connected to a piston-engine piston-trigger shaft arranged in the engine-emitter piston relaxation by a piston rod trigger relaxation, said crank shaft cooperating with transmission means secondary detent including a sprocket gear transmission and a trigger transmission rack.
• FIGS. 5 and 6 are diagrammatic sections illustrating the operation of the end-of-travel regulator for a piston pressure converter according to the present invention and in a variant in which the progressive-action lever transmission consists of a crank shaft comprising a crank trigger-emitting piston piston whose crank pin is connected to a piston-engine piston-trigger shaft arranged in the engine-emitter piston relaxation by a piston rod trigger relaxation, said crank shaft cooperating with transmission means secondary detent notably consisting of a relaxation receiver piston crank whose crank pin is connected to a pump-receiver piston pin relaxation arranged in the piston pump-relaxation receiver by a piston rod relaxation receiver.
• FIGS. 5 and 6 are diagrammatic sections illustrating the operation of the end-of-travel regulator for a piston pressure converter according to the present invention and in a variant in which the progressive-action lever transmission consists of a crank shaft comprising a crank trigger-emitting piston piston whose crank pin is connected to a piston-engine piston-trigger shaft arranged in the engine-emitter
• FIGS. 7 and 8 are diagrammatic sections illustrating the operation of the end-of-stroke regulator for a piston pressure converter according to the present invention and in a variant in which the progressive-action lever transmission consists of a camshaft comprising a cam a trigger-emitting piston piston that can be held in contact with the engine-trigger piston, and a trigger-receiving piston cam that can be held in contact with the pump-trigger piston.
• the progressive-action lever transmission consists of a camshaft comprising a cam a trigger-emitting piston piston that can be held in contact with the engine-trigger piston, and a trigger-receiving piston cam that can be held in contact with the pump-trigger piston.
• FIGS. 1 to 8 show the end-of-stroke pressure 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 variable volume chamber 9 which can be put into connection with an intake duct 22 by an intake valve 18 or with an emitter discharge duct 23 via a discharge valve d transmitter 19, said pressure converter 2 also comprising at least one receiver cylinder 4 in which a pump-receiver piston 8 can be moved so as to define a receiving chamber 10 also of variable volume, the latter being able to admit a hydraulic fluid coming from of a receiver intake duct 24 via a receiver inlet valve 20 or refolding said fluid in a receiver discharge pipe 25 via a receiver discharge valve 21, the emitting chamber 9 and the receiving chamber 10 being each filled with a hydraulic fluid.
• FIGS. 1 and 2 show that the end-of-stroke regulator 1 according to the invention comprises at least one trigger-emitting cylinder 12, filled with a hydraulic fluid, and in which a motor-emitter piston can be displaced. 14 so as to define a triggering chamber 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 6 can communicate - as the case may be - either with the emitter chamber 9 or with the receiving chamber 10 via a conduit 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 terminate at the inner surface of a cylinder cylinder cylinder 5 capping the emitter cylinder 3 or at the inner surface of a receiver cylinder head 6 capping the receiver cylinder 4. It will also be noted in FIGS.
• the end-of-stroke regulator 1 comprises at least one expansion receiver cylinder 13 which cooperates with the expansion emitter cylinder 12 and in which a pump-receiver piston can move.
• detent 15 so as to define with said receiving cylinder 13 an expansion receiver chamber 17 of variable volume filled with a hydraulic fluid, said pump-receiver piston 15 being mechanically connected to the engine piston-trigger 14 by a lever transmission with progressive effect 1 1 arranged so that when the piston engine-emitter relaxation 14 is at the top dead center, the piston-receiver piston 15 is in the low dead center and vice versa, while the maximum volume of the receiving chamber of relaxation 17 is lower than the maximum volume of the expansion 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 more engine piston-trigger transmitter 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 piston 15 may comprise at least one seal and / or at least one segment of etan chéiîé.
• FIGS. 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 a trigger receiver admission duct 28 to enter said receiving chamber 7 but not out.
• FIGS. 1 to 8 also show that the end-of-stroke regulator 1 comprises at least one expansion receiver discharge port 27 which opens into the expansion receiver chamber 17 and which allows a fluid hydraulic contained in a detent receiver delivery conduit 28 to exit said chamber ré ⁇ ptri ' ⁇ 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 the cylinder 13 if it is blind. It will be noted in FIGS.
• the end-of-stroke regulator 1 also comprises at least one trigger release actuator 30 that can, by contact or mechanical connection, set in motion the progressive-action lever transmission 1 1 or unblock the latter so as to set in motion the piston motor-emitter relaxation 14 and the piston pump-recess 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 transmission ratio between said pistons 14, 15 sufficient for the piston-emitter relaxation 14 can continue its race without the aid of trigger release actuator 30.
• trigger release actuator 30 can, by contact or mechanical connection, set in motion the progressive-action lever transmission 1 1 or unblock the latter so as to set in motion the piston motor-emitter relaxation 14 and the piston pump-recess 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 transmission ratio between said pistons 14, 15 sufficient for the piston-emitter relaxation 14 can continue its race without the aid of trigger release actuator 30.
• the trigger release accelerator 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 admission valve 26 to the expansion receiver chamber 17 cooperating with the variable-volume expansion chamber 16 which communicates with the receiving chamber 10 can be connected to the receiver intake duct 24 while the expansion receiver discharge duct 28 connected to the same said expansion receiver chamber 17 can be connected to the receiver rejection duct 25.
• the expansion receiver intake duct 28 connected via the expansion receiver intake valve 26 the relaxation receiving chamber 17 cooperating with the trigger 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-action lever transmission 11 may comprise a return spring for the expansion pistons 33 which tends to maintain the engine-emitter relaxation piston 14 in the vicinity of its position where the emitter chamber the expansion valve 16 has the smallest volume while simultaneously, said spring 33 keeps the pump piston-receiver relaxation in the vicinity of its position where the trigger receiver chamber 17 has the largest volume, said spring 33 can be of torsion, flexion, traction or compression and be of any type known to those skilled in the art.
• FIGS. 3 to 6 show that, according to the end-of-travel regulator 1 according to the invention, the progressive-action lever transmission 11 may consist of a crankshaft 46 that can rotate in a shaft bearing at crank 47 and comprising a trigger-emitting piston maneuver 35 whose crank pin 48 is connected to a piston-engine piston-rest axis 49 arranged in the engine-emitter piston relaxation 14 by a piston rod relaxation transmitter 34 whose first end is articulated around said crank pin 48 and whose second end is articulated around said axis 49, the crank shaft 48 cooperating with secondary expansion means of transmission 51 which mechanically connect said shaft 48 with the pump-receiver piston relaxing 15.
• FIGS. 3 and 4 show that the secondary triggering transmission means 51 may consist of an expansion gear toothed wheel 36 which is integral in rotation with the crankshaft 46 and which, when it rotates, drives in linear translation. an expansion transmission rack 37 connected to the pump-receiver piston 15 directly or by means of a trigger piston piston push rod 39.
• the trigger transmission rack 37 can be guided, in particular by at least one trigger rack guide gaiet 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 piston pump-trigger relaxation piston axis 50 arranged in the pump piston-trigger receiver 15 by a piston rod relaxation receiver 41 whose first end is articulated around said crank pin 48 and whose second end is articulated around said axle 50. It is readily conceivable that, according to a variant not shown, the secondary triggering transmission means 51 may also consist of a cam integral in rotation with the crankshaft 46 and able to be kept in contact with the piston.
• 1 progressive effect lever mechanism can be consisting of 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-emitter piston 14 and a piston-receiver cam detent 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 comprising a crankpin connected to a shaft arranged in the piston pump-trigger receiver 15 by a connecting rod whose first end is articulated around otuet 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 34 or the rebound-transmitting gearbox 37 or the receiver piston crank 40 or the trigger piston piston rod 41 or the camshaft 52 or the defending emitter piston cam 42 or the trigger piston piston cam 43 may have an expansion 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 pump piston-trigger receiver 15 when the piston engine-emitter relaxation 14 is placed in its top dead center or in the vicinity of the latter.
• FIGS. 1 to 8 show a variant according to which the trigger release push-button 32 is provided on the trigger-emitting piston crank 35.
• FIGS. 1 and 2 Two configurations of which are schematically represented. in FIGS. 1 and 2.
• FIGS. 1 and 2 For simplicity, we will consider mainly the diagram of FIG. 1 which exposes a piston pressure converter 2 with a single emitting chamber 9 and a single receiving chamber 10.
• the purpose of the application illustrated in FIG. 1 is to convert stored energy in the form of compressed nitrogen into a tank of high-pressure fluid 58 into electricity by means of an electricity generator 62 driven by an engine. Hydraulic medium-pressure 59.
• the compressed nitrogen communicates its pressure to a hydraulic fluid that can in particular circulate in the conduits 54.
• a piston pressure converter 2 has been inserted between the high-pressure fluid reservoir 58 and the medium-pressure hydraulic motor 59 and converts a high-pressure flow rate of hydraulic fluid leaving the reservoir 58 a medium-pressure flow 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. W
• the high-pressure fluid reservoir 58 in order to generate a mean-pressure flow rate of the hydraulic fluid entering the medium-pressure hydraulic motor 59, the high-pressure fluid reservoir 58 must be put in communication with the emitter chamber 9.
• the control computer of the pressure converter 55 opens the emitter admission valve 18 which allows the hydraulic fluid contained in the high-pressure fluid reservoir 58 to enter the emitter chamber 9 via the intake duct.
• said calculator 55 simultaneously prevents said fluid from exiting said chamber 9 to go to the low-pressure transmitter output fluid reservoir 5ô, said calculator 55 now 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 2, 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 powpe-reeceiver piston 8 compresses the hydraulic fluid contained in the receiving chamber 10, which has the effect of expelling said fluid in the discharge pipe of the receiver 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 52, 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 can no longer definitively be transformed into additional flow of hydraulic fluid leaving the receiver discharge pipe 25.
• the end-of-stroke 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 9 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 control unit of the pressure converter 55 supplies the expansion release valve 30 with electric current, which has the effect of setting the lever transmission in motion. progressive effect 1 1 and therefore, to set in motion the piston-emitter relaxation 14 and the pump-receiver piston relaxation 15, the engine piston-emitter 14 is previously parked in its top dead center.
• FIG. which was the limit valve 1 according to the invention as the piston engine-emitter 7 and the pump-receiver piston 8 were moving in the direction d2. It should be noted that the engine-emitter piston 14 remains blocked 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 engine-emitter piston 7 and the piston pump-receiver 8 are temporarily stopped.
• the pressure in the emitter chamber 9 corresponds approximately to the pressure in the high pressure fluid reservoir 58 that however ia pressure prevailing in its 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 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 crankshaft 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 cross-section and the variable transmission ratio between the piston engine-expander 14 and the pump piston-receiver relaxation 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 an additional medium-pressure hydraulic fluid flow rate 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 piston pump-receiver for the latter to produce the desired pressure in the expansion receiver chamber 17.
• the instantaneous ratio of transmission between the engine-emitter piston relaxation 14 and the pump-receiver piston relaxation is 15 - 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 ie the expansion receiver discharge duct 29 via the expansion receiver discharge valve 27.
• the motor-emitter piston 7 and the pump-receiver piston 8 begin to advance substantially in the direction c
• the operating piston-expansion piston 14 moves towards its bottom dead point while decreasing the pressure it receives from the hydraulic fluid 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 valve As a result, the motor-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 fluid reservoir. Receiver inlet low-pressure 63 over the entire section of the pump-receiver piston 8, via the receiver inlet valve 20.
• the emitter 7 arrives near the emitter cylinder head 5, ie the pressure converter management computer 55 closes the emitter discharge valve 19 and the engine-emitter piston 7 and the pump-receiver piston 8 cease to move around. the meaning dl.
• 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 5 returns to its bottom dead center by sucking - via the expansion receiver intake valve 26 - hydraulic fluid from the receiver low-pressure fluid reservoir 63 so as to fill the
• 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 tank of 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 end up in a hydraulic fluid tank 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 will arrive again near the receiver cylinder head 5.

Landscapes

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

Applications Claiming Priority (3)

Publications (2)

Family

ID=51261066

Family Applications (1)

Country Status (10)

Families Citing this family (7)

Family Cites Families (20)

• 2014
  • 2014-05-12 FR FR1454223A patent/FR3020840B1/fr active Active
  • 2014-06-20 FR FR1455710A patent/FR3020841B1/fr active Active
• 2015
  • 2015-05-07 CA CA2946466A patent/CA2946466C/fr active Active
  • 2015-05-07 ES ES15732299T patent/ES2709397T3/es active Active
  • 2015-05-07 AU AU2015261366A patent/AU2015261366B2/en active Active
  • 2015-05-07 CN CN201580024795.2A patent/CN106662082B/zh active Active
  • 2015-05-07 WO PCT/FR2015/051209 patent/WO2015173495A1/fr active Application Filing
  • 2015-05-07 EP EP15732299.1A patent/EP3143288B1/de active Active
  • 2015-05-07 KR KR1020167031252A patent/KR102277604B1/ko active IP Right Grant
  • 2015-05-07 JP JP2016563464A patent/JP6559704B2/ja active Active
  • 2015-05-11 US US14/709,036 patent/US9856891B2/en active Active

Also Published As

Similar Documents

Legal Events