EP0192580A1 - Flüssigkeitsdruckverstärker - Google Patents

Flüssigkeitsdruckverstärker Download PDF

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Publication number
EP0192580A1
EP0192580A1 EP86420006A EP86420006A EP0192580A1 EP 0192580 A1 EP0192580 A1 EP 0192580A1 EP 86420006 A EP86420006 A EP 86420006A EP 86420006 A EP86420006 A EP 86420006A EP 0192580 A1 EP0192580 A1 EP 0192580A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
annular chamber
section
hydraulic pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP86420006A
Other languages
English (en)
French (fr)
Inventor
Jean-Claude Simon Barthomeuf
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
EIMCO-SECOMA
Eimco Secoma SA
Original Assignee
EIMCO-SECOMA
Eimco Secoma SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by EIMCO-SECOMA, Eimco Secoma SA filed Critical EIMCO-SECOMA
Publication of EP0192580A1 publication Critical patent/EP0192580A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04B9/109—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 plural pumping chambers
    • F04B9/111—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 plural pumping chambers with two mechanically connected pumping members
    • F04B9/113—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 plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by a double-acting liquid motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/066—Arrangements with main and auxiliary valves, at least one of them being fluid-driven piston or piston-rod being used as auxiliary valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure

Definitions

  • the present invention relates to a hydraulic pressure booster, that is to say an apparatus receiving its energy from a hydraulic fluid under pressure, called “primary fluid”, and transferring this energy to another hydraulic fluid, called “secondary fluid ", so as to obtain a flow rate of this other fluid under a pressure greater than that of the primary fluid.
  • primary fluid a hydraulic fluid under pressure
  • secondary fluid another hydraulic fluid
  • the invention relates to a pressure amplifier capable of providing a permanent flow of water under high pressure, usable in applications such as the drilling of rocks or the cutting of other materials, either in assistance of mechanical means , or in the form of a cutting jet used alone.
  • Hydraulic pressure amplifiers are also known, making it possible to reach higher water pressures, of the order of 4,000 bars, the principle of which is as follows: a piston is slidably mounted in a cylinder, forming a share and on the other side of the piston two chambers in which oil under pressure is admitted alternately.
  • the piston is extended, on its two opposite faces, by two plungers which slide in respective cylindrical chambers, each comprising an inlet and a outlet for water.
  • the reciprocating movement of the piston under the effect of the thrust of the oil constituting the primary fluid, is accompanied by alternating displacements of the two plungers in the corresponding chambers, ensuring the pressurization of the water constituting the secondary fluid.
  • the pressure thus obtained for this secondary fluid is multiple of that of the primary fluid, the ratio of pressures being equal to the ratio of the section of the piston to the section of the plungers. This ratio can be of the order of 10 to 20.
  • the object of the present invention is to simplify these devices, by a total elimination of all limit switches and by arrangements allowing autonomous operation, without auxiliary organs, controlling the supply of primary fluid to the chambers of the cylinder in which slides the piston being made from the movements of the piston itself, this by purely hydraulic means.
  • the hydraulic pressure booster essentially comprises a stepped piston slidably mounted inside a cylinder so as to form a first annular chamber, of smaller section, permanently connected to a supply. of a primary fluid under pressure, and a second annular chamber, of larger section, connected to a control valve with differential section slide, putting said second annular chamber in communication alternately with the supply of primary fluid under pressure and with a return pipe for this fluid, the control of the control valve being ensured by the primary fluid by means of a single pipe whose outlet in the cylinder is alternately uncovered and masked by the piston, this piston being extended along its axis , at its two ends, by two plungers of smaller section penetrating respectively into two chambers connected, by means of valves, with arrivals and departures of a secondary fluid.
  • the primary fluid the energy of which is transmitted to the piston, also ensures the control of the control valve, the operation being entirely hydraulic so that all mechanical or electrical means for detecting the end of travel and for control become unnecessary.
  • the piston moving in one direction reaches one of its end-of-travel positions, it automatically causes the valve of the control valve to move, modifying the hydraulic connections so as to cause the piston to move in the opposite direction.
  • the piston thus describes a back-and-forth movement which maintains itself, and the two plungers of section smaller than the section of the piston itself cause the pressurization of the secondary fluid. re, one diver in two is still in action.
  • the piston proper and the two plungers extending it at its ends, form a one-piece structure, in which the plungers can also contribute to the delimitation of the annular chambers.
  • the piston has a cylindrical part of intermediate diameter, around which the first annular chamber of the cylinder is formed, of smaller section, and a cylindrical part of small diameter, around which the second chamber is formed. annular of the cylinder, of larger section.
  • the section of the first annular chamber of the cylinder is equal to half the section of the second annular chamber of the cylinder, which makes it possible to obtain equal thrusts and in opposite directions on the piston: in its first direction of displacement, obtained when only the first annular chamber of the cylinder is connected to the supply of primary fluid under pressure, and in its second direction of movement, obtained when the two annular chambers of the cylinder are connected to the supply of primary fluid under pressure .
  • the operation is perfectly “symmetrical” which makes it possible to obtain the same pressure of the secondary fluid, in the "go" movement and in the "return” movement of the piston (the sections of the two plungers being of course equal) .
  • the cylindrical part of larger diameter of the piston has an annular groove
  • the wall of the cylinder has an orifice connected to the return pipe of the primary fluid and located in such a way that, in an end of travel position of the piston, communication is established between the pilot valve control conduit and said return conduit.
  • the control valve advantageously comprises a drawer having two intermediate spans of relatively large section and two ends of smaller sections, the drawer being slidably mounted in a cavity forming, around the drawer, three annular distribution chambers connected respectively to the supply of primary fluid under pressure, to the return duct of this fluid and to the second annular chamber, of larger section, of the cylinder, as well as a fourth annular chamber connected to the cylinder by the pilot duct, the valve putting the third chamber distribution in communication, depending on the position of the drawer, either with the first distribution chamber or with the second distribution chamber.
  • the valve of the control valve has two ends of separate sections, slidably mounted in two respective cylindrical chambers of corresponding sections, into which the primary fluid under pressure is permanently admitted, for example by providing an axial passage extending from one end to the other of the drawer and communicating, by a nozzle, with the lateral surface of this drawer, at the level of the first distribution chamber.
  • the slide is pushed to a position determined by the pressure of the primary fluid acting on its two ends, when the pilot chamber is not pressurized.
  • a single pilot hole in the cylinder is sufficient, allowing the pilot chamber to be pressurized, to move the piston to its other position.
  • the control conduit of the control valve is advantageously connected, permanently, to an accumulator making it possible to maintain the control chamber under pressure during the entire stroke of the piston, by compensating for internal leaks.
  • Another accumulator can be connected to the first annular chamber of the cylinder, permanently, and to the second annular chamber of the cylinder when the latter is placed in communication with the supply of primary fluid under pressure by the control valve; this second accumulator dampens the movements of the piston at the end of the stroke, and restores energy to the piston when it starts again in the opposite direction.
  • It can also be formed, around the piston and / or the plungers, between the cylinder and the two chambers into which the plungers penetrate, two auxiliary annular chambers with outlets, avoiding any mixing of the primary fluid and the secondary fluid.
  • the outlets of the two chambers supplied with this fluid, into which the two plungers respectively penetrate, are united in a single conduit from which an accumulator is provided. This gives a substantially constant flow of secondary fluid under high pressure, substantially constant, which can be directed to the place of use of this secondary fluid.
  • a first cylindrical chamber (2) is formed, in communication with a first water inlet orifice (3) and with a first water outlet orifice (4 ).
  • a second cylindrical chamber (5) is provided at the opposite end of the body (1), in commu- nica t ion with a second water inlet (6) and a second water outlet ( 7), the arrangement being symmetrical with respect to that of the first end.
  • Supply valves (8,9) are placed between each water inlet orifice (3,6) and the corresponding cylindrical chamber (2,5).
  • Discharge valves (10,11) are placed between each cylindrical chamber (2,5) and the corresponding water outlet orifice (4,7).
  • the two water outlet orifices (4,7) are connected, by respective conduits (12,13), from a single conduit (14) directed towards the place of use of the water under high pressure .
  • An accumulator (15) is provided at the start of this latter conduit (1 4 ).
  • the two cylindrical chambers (2,5) are of the same section and arranged along the same axis (16).
  • a cylinder (17) of larger section is hollowed out in the body (1), along this axis (16), between the two cylindrical chambers (2,5).
  • Inside the cylinder (17) is slidably mounted, in the direction of the axis (16), a piston (18) extended, at its ends, by two opposite plungers (19,20), the piston (18) and the plungers (19,20) forming a one-piece structure.
  • the first plunger (19) enters the first cylindrical chamber (2).
  • the second plunger (20) enters the second cylindrical chamber (5).
  • the piston (18) has a stepped shape, with a cylindrical part (20a) of small diameter, a cylindrical part (21) of intermediate diameter and another cylindrical part (22) of larger diameter, in which an annular groove is hollowed out. (23).
  • This conformation of the piston (18) defines inside the cylinder (17), a first annular chamber (24) of section (SI), located around the part (21), and a second annular chamber (25) of section (S2 ), located around part (20a).
  • the two plungers (19,20) are of the same section, much smaller than the previous sections (S1, S2) and can be equal to that of the cylindrical part (20a).
  • an auxiliary annular chamber (28), with evacuation orifice (29), avoiding any mixing of fluids.
  • An auxiliary annular chamber (30) with the same function as the previous one, although of smaller dimensions, is also formed between the cylinder (17) and the second cylindrical chamber (5).
  • the cylinder (17) is designed to receive a hydraulic fluid called "primary fluid", such as oil, capable of causing the reciprocating movement of the piston (18).
  • the first annular chamber (24), of section (S1) is permanently connected to an inlet for pressurized oil (at 31), by a conduit (32) which opens into the chamber considered (24).
  • the second annular chamber (25), of section (S2) is connected either with the arrival of oil under pressure (at 31), or with the departure of the oil towards the reservoir (at 33), this via a control valve (34).
  • the control valve (34) comprises a drawer (35) slidably mounted in a body cavity (1), forming around the drawer (35) three coaxial annular distribution chambers (36,37,38).
  • a first distribution chamber (36) is connected by a channel (39) to a point in the conduit (32) for supplying pressurized oil.
  • a second distribution chamber (37) is connected, by a return pipe (40), to the flow of oil to the tank (at 33).
  • a third distribution chamber (38), located between the two preceding ones (36,37), is connected by a channel (41) to the second annular chamber (25), of section (52), of the cylinder (17).
  • the drawer (35) has two intermediate spans of large section (S). It has an end of small section (S '), sliding in a cylindrical chamber (42). Its other end, of section (S ") intermediate between the preceding sections (S and S '), slides in a cylindrical chamber (43).
  • the drawer (35) still has a passage axial (44) which extends from one end to the other of this drawer (35) and which communicates, by a lateral nozzle (45), with the lateral surface of this drawer, at the level of the first distribution chamber (36).
  • annular chamber (46) Around the first end of the slide (35) is also formed an annular chamber (46), put in communication with the cylinder (17) by a pilot duct (47) starting from a pilot orifice ( 4 8) located in an intermediate point of the length of the cylinder (17).
  • pilot orifice ( 4 8) located in an intermediate point of the length of the cylinder (17).
  • Another orifice (49) of the cylinder (17) close to the previous one, constitutes the starting point of a channel (50) which meets the return duct (40).
  • first accumulator (53) being in connection with the cylinder (17), and with the pilot duct (47), and the second accumulator (54) being in connection with the conduit (32) for supplying pressurized oil, here via the first distribution chamber (36) and the channel (39).
  • the axial passage (44) and the lateral nozzle (45) of the drawer (35) ensure the permanent presence of oil under pressure in the two cylindrical chambers (42,43) housing the ends of the drawer (35). If the annular chamber (46) is connected at the reservoir, the slide (35) is subjected to a first thrust, due to the oil pressure in the chamber (42) acting on the section (S '), and to a second thrust in the opposite direction, due to the oil pressure in the chamber ( 4 , 3) being exerted on the section (S ").
  • the section- (S") being greater than the section (S '), the result of the two thrusts considered is a force oriented to the left.
  • the piston (18) moves from left to right, the second annular chamber (25) of the cylinder (17) being connected to the reservoir taking into account the position of the drawer (35) of the valve (34), position determined by the fact that the annular chamber (46) is also connected to the reservoir.
  • Pressurizing the second annular chamber (25) then causes the piston (18) to move to the right.
  • the pilot orifice (48) is masked by the cylindrical part (22) of the piston (18), so that the drawer (35) of the valve (34) remains in its position indicated in the figure 1.
  • the drawer (35) is thus pushed to the left (position indicated in Figure 2).
  • the position of the two intermediate spans of the drawer (35) then becomes such that the second distribution chamber (37) is placed in direct communication with the third distribution chamber (3S), while the first distribution chamber (36) is isolated from the third distribution chamber (38).
  • the second annular chamber (25) of the cylinder (17) is connected with the flow of oil to the reservoir (at 33), this through the channel (41), of the third chamber distribution (38), the second distribution chamber (37) and the return duct (40).
  • This water is for example used to obtain a cutting jet, in mining applications such as rock drilling, either carried out entirely by a water jet, or only assisted by a water jet.
  • the accumulator (53) which is always in relation to the pilot duct (47), makes it possible to stabilize the pressure in the annular chamber (46), and avoids any influence of internal oil leaks on the piloting of the valve (34).
  • This accumulator (53) allows the piston (18) to describe a relatively large stroke at a relatively low speed.
  • the accumulator (54) its function is to dampen the movement of the piston when approaching the end positions of the left and right, by accumulating energy and restoring it again.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Reciprocating Pumps (AREA)
EP86420006A 1985-01-09 1986-01-08 Flüssigkeitsdruckverstärker Withdrawn EP0192580A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8500540 1985-01-09
FR8500540A FR2575792A1 (fr) 1985-01-09 1985-01-09 Amplificateur de pression hydraulique

Publications (1)

Publication Number Publication Date
EP0192580A1 true EP0192580A1 (de) 1986-08-27

Family

ID=9315307

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86420006A Withdrawn EP0192580A1 (de) 1985-01-09 1986-01-08 Flüssigkeitsdruckverstärker

Country Status (6)

Country Link
US (1) US4659294A (de)
EP (1) EP0192580A1 (de)
JP (1) JPS61197801A (de)
AU (1) AU5214186A (de)
FR (1) FR2575792A1 (de)
ZA (1) ZA8646B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103038499B (zh) * 2010-06-21 2016-11-16 水动力科技有限公司 流体压力放大器

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US5388725A (en) * 1993-11-24 1995-02-14 Fountain Fresh International Fluid-driven apparatus for dispensing plural fluids in a precise proportion
JPH08281571A (ja) * 1995-04-14 1996-10-29 Komatsu Ltd 振動発生装置
US5787998A (en) * 1995-08-03 1998-08-04 Flowdril Corporation Down hole pressure intensifier and drilling assembly and method
GB2346178B (en) * 1999-01-26 2003-03-19 Brian William Young Integral pump and control valve
US6729860B1 (en) * 2000-01-24 2004-05-04 Daniel A. Holt Pneumatically driven liquified gas booster pump
EP1358407A4 (de) * 2001-01-19 2004-08-11 Munters Corp Hochdruckwasserpumpe
ES2219122B1 (es) * 2001-07-27 2005-09-16 Bolsaplast, S.A. Bomba para sistemas desalinizadores de agua marina por osmosis inversa.
DE10158182B4 (de) * 2001-11-28 2005-06-02 Minibooster Hydraulics A/S Doppeltwirkender hydraulischer Druckverstärker
DE10249523C5 (de) * 2002-10-23 2015-12-24 Minibooster Hydraulics A/S Druckverstärker
DE102004042369A1 (de) * 2004-09-01 2006-07-13 Eurodrill Gmbh Bodenbearbeitungsgerät und Verfahren zum Einbringen eines Arbeitselementes in den Boden
DE102006038862A1 (de) * 2006-08-18 2008-02-21 Scanwill Aps Druckübersetzer mit Doppelsitzventil
US8695414B2 (en) 2011-07-12 2014-04-15 Halliburton Energy Services, Inc. High pressure and flow rate pump useful in formation fluid sample testing
FR3009849B1 (fr) 2013-08-20 2016-03-11 Vianney Rabhi Convertisseur de pression hydraulique reversible a vannes tubulaires
US9695840B2 (en) 2013-08-20 2017-07-04 Vianney Rabhi Reversible hydraulic pressure converter employing tubular valves
BR102013024307B1 (pt) * 2013-09-23 2022-03-29 Drausuisse Brasil Comércio E Locação De Unidades Hidráulicas Inteligentes S.A. Unidade geradora de pressão hidráulica com acionamento pneumático
DE102014006759A1 (de) * 2014-05-08 2015-11-12 Dürr Systems GmbH Abluftführung für eine Beschichtungsmittelpumpe
AT516738B1 (de) * 2015-02-23 2016-08-15 Reinhard Ing Gruber Verfahren und Vorrichtung zum Betreiben einer hydraulischen Hochdruckanlage
CH711414A1 (de) * 2015-08-13 2017-02-15 Hatebur Umformmaschinen Ag Vorrichtung zur Erzeugung impulsdynamischer Prozesskräfte.
ES2736135T3 (es) * 2017-03-03 2019-12-26 Pistonpower Aps Amplificador de presión
ES2736402T3 (es) 2017-03-03 2019-12-30 Pistonpower Aps Intensificador de presión hidráulica de doble acción
ES2734307T3 (es) 2017-03-03 2019-12-05 Pistonpower Aps Intensificador de presión hidráulica
EP3369929B1 (de) 2017-03-03 2019-04-24 PistonPower ApS Druckverstärker
CN107476915B (zh) * 2017-08-22 2019-11-01 哈尔滨工程大学 一种带缓冲装置的双作用式高压燃油供给装置
DE102019109486B4 (de) * 2019-04-10 2022-12-22 RED Drilling & Services GmbH Vorrichtung zum Erhöhen eines Drucks eines Arbeitsfluids für ein Bohrsystem
WO2020227306A1 (en) * 2019-05-06 2020-11-12 Schlumberger Technology Corporation High-pressure drilling assembly
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FR1360978A (fr) * 1963-06-19 1964-05-15 Keelavite Hydraulics Ltd Appareil hydraulique alternatif
FR1488575A (fr) * 1965-09-14 1967-07-13 Sulzer Ag Dispositif pour l'injection du carburant dans un moteur à combustion interne à pistons
FR2305279A1 (fr) * 1975-03-22 1976-10-22 Klemm Bohrtech Appareil de frappe hydraulique
FR2352175A1 (fr) * 1976-05-21 1977-12-16 Hausherr & Soehne Maschf Pompe a haute pression
GB2117845A (en) * 1982-04-03 1983-10-19 Af Hydraulics Hydraulic percussive apparatus

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103038499B (zh) * 2010-06-21 2016-11-16 水动力科技有限公司 流体压力放大器

Also Published As

Publication number Publication date
JPS61197801A (ja) 1986-09-02
FR2575792A1 (fr) 1986-07-11
US4659294A (en) 1987-04-21
ZA8646B (en) 1986-08-27
AU5214186A (en) 1986-07-17

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