EP1048849B1 - High pressure liquid pump - Google Patents

High pressure liquid pump Download PDF

Info

Publication number
EP1048849B1
EP1048849B1 EP00202790A EP00202790A EP1048849B1 EP 1048849 B1 EP1048849 B1 EP 1048849B1 EP 00202790 A EP00202790 A EP 00202790A EP 00202790 A EP00202790 A EP 00202790A EP 1048849 B1 EP1048849 B1 EP 1048849B1
Authority
EP
European Patent Office
Prior art keywords
pump
chamber
membrane
liquid
piston
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.)
Expired - Lifetime
Application number
EP00202790A
Other languages
German (de)
French (fr)
Other versions
EP1048849A1 (en
Inventor
Louis-Claude Porel
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.)
Hydro Leduc SAS
Original Assignee
Hydro Leduc SAS
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
Priority claimed from FR9607043A external-priority patent/FR2749616B1/en
Priority claimed from FR9613502A external-priority patent/FR2755472B1/en
Application filed by Hydro Leduc SAS filed Critical Hydro Leduc SAS
Publication of EP1048849A1 publication Critical patent/EP1048849A1/en
Application granted granted Critical
Publication of EP1048849B1 publication Critical patent/EP1048849B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • F02M59/246—Mechanisms therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/04—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by special arrangement of cylinders with respect to piston-driving shaft, e.g. arranged parallel to that shaft or swash-plate type pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/08—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by two or more pumping elements with conjoint outlet or several pumping elements feeding one engine cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/12—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps having other positive-displacement pumping elements, e.g. rotary
    • F02M59/14—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps having other positive-displacement pumping elements, e.g. rotary of elastic-wall type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/243—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movement of cylinders relative to their pistons
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • 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
    • F04B43/00—Machines, pumps, or pumping installations having flexible working members
    • F04B43/02—Machines, pumps, or pumping installations having flexible working members having plate-like flexible members, e.g. diaphragms
    • F04B43/06—Pumps having fluid drive
    • F04B43/067—Pumps having fluid drive the fluid being actuated directly by a piston
    • 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
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/142—Intermediate liquid-piston between a driving piston and a driven piston

Definitions

  • the free pistons have a defect with regard to the sealing, a defect which is essential in the case where one must have an absolute seal. If we put in place a seal between the free piston and the cylinder in which it moves, it is not possible to obtain a perfect seal. If we remove the seal: or there is has a very thin film of oil between the friction surfaces and therefore micro-leaks: or there is no oil film and the friction surfaces will heat up. In the particular case of high-pressure gasoline injection no leak, also little is it, is not admissible and, of course, any warm-up risk of cause an explosion.
  • the present invention thus relates to a pumping device in which the moving elements, driven by an alternating movement of pumping by the pump hydraulic and ensuring a completely sealed separation between the liquid Hydraulic "motor” and the liquid to be pumped are deformable membranes.
  • German Patent 2,447,741 WANNER a diaphragm pump has been described. which is mechanically linked to a piston which slides inside a piston of hydraulic pump.
  • the disadvantages are the same as for the patent US 4,392,787 cited above.
  • the present invention proposes a device in which which each membrane is free and in which, at the end of each cycle of a piston, the dead chamber, located downstream of the top dead center of this piston (position maximum compression), in which is the liquid in contact with the membrane is put into communication with the reserve of hydraulic fluid; of so that the liquid which is there is pushed back towards this reserve first by the relaxation of the liquid, then by the effect of repression by the membrane which is corum by a spring.
  • the present invention relates to a pump for pump any kind of liquid while printing a pressure of very high discharge, of the type constituted by the association of two pumps: on the one hand, a hydraulic pump; on the other hand, a second pump whose moving means, carrying out the suction and the delivery of the liquid to be pumped, are flexible membranes animated with a reciprocating motion in a more direction in the other by the displacement of the hydraulic fluid pumped and then sucked by the first pump characterized by the fact that the pistons of the first pump are hollow and traversed by the hydraulic fluid which, during the suction phase crosses a lunula or groove dug in the face of the bias or cam plate; the deformable membranes being each controlled by a spring so that that at the end of the compression stroke of each piston, the communication is between the chamber where the hydraulic fluid is pushed back against the membrane and the suction chamber, this liquid being, on the one hand, sucked by the movement of the piston and pushed back by the membrane under the action of its spring,
  • the present invention relates to means for vary the displacement of the first pump and therefore the flow of gasoline to the injection devices.
  • variable inclination bias tray or the arrangement of means in the pistons of the hydraulic pump, having for function to short-circuit all or part of the volume of hydraulic fluid introduced into the bore during the suction phase.
  • each hollow piston of the hydraulic pump is provided with openings that can be obscured in whole or in part by a mobile shirt, all the moving jackets being moved together by a control member subject to the operating conditions of the engine.
  • the device according to the invention comprises a first pump, designated by the general reference I and a second pump, designated by the general reference II.
  • the first pump I is an axial piston pump driven by a movement alternate back-and-forth by a bias tray 1.
  • the bias plate 1 is integral with a drive shaft 2 (driven by any means not shown) carried by bearings 3.
  • a plurality of hollow pistons 4 take support against the oblique face of the plate 1 each by means of a sliding block 5, which is pierced at its center with a bore 6.
  • Each piston 4 is held by a spring 7 against his stud.
  • On the front face 1 is engraved a lunula 8.
  • This room 9 opens, through a plurality of holes 22, through the body 21 of the pump 1, in a tank 11.
  • This tank 11 is constituted by a cylindrical envelope 23 surrounding the body 21.
  • the side of the bias plate 1 oscillates in the chamber 9 so that the pistons 4 are driven reciprocating back and forth: in the direction corresponding to the suction, the pistons 4 are driven by their spring 7; in the other direction which corresponds to the repression under pressure, they are pushed back to against the spring 7 by the bias plate 1.
  • the hydraulic fluid that is in the chamber 9 gets inside the pistons 4 passing through the lunula 8 and the bore 6 of the studs 5.
  • each bore 12 in which slides a hollow piston 4 has at its end a non-return valve ; so that all of said pistons 4 causes a flow under pressure (and even under high pressure since one can exceed 1000 bars with this type of pump).
  • none of the bores 12 in which slide the pistons 4 has a non-return valve.
  • a pump 1 is associated with the pump I immediately downstream thereof.
  • each bore 2 of the pump I corresponds, in the pump II, a chamber or bore 13 divided into two parts 13a and 13b by a flexible membrane 24 biased by a spring 15.
  • the part 13a communicates directly with the end of the bore 12, while the portion 13b is provided with its end opposite the membrane 24 of a suction valve 16 and a valve 17. All valves 17 flow in a common pipe 18.
  • each spring 15 is supported on the rear face of the membrane 24 via a cup 20.
  • the shape of the cup 20 is determined so that the support of the cup 20 on the face rear of the membrane 24 does not cause any deterioration thereof.
  • the displacement of the membrane 24 in the direction of the arrow f2 has the effect to suck the product to be pumped into the part 13b of the bore 13, through the valve anti-return valve 16 and to discharge the hydraulic fluid in the part 13a.
  • Each membrane 24 is subjected on its two front and rear faces and that of uniformly distributed over the entire surface of the membrane, at the same pressure: on one side the pressure of the engine hydraulic fluid, on the other hand the pressure of the liquid discharged. The membrane therefore undergoes no mechanical effort and therefore can not tear.
  • the pump according to the present invention is therefore a diaphragm pump in which each membrane is, in the phase of repression, an equipression of each side which allows to have a pressure of discharge equal to the pressure hydraulic that can provide the first pump I.
  • liquids can no longer be considered as incompressible.
  • the hydraulic fluid pressure is at its maximum.
  • the stud 5 is on the beginning of the lunula 8 the liquid, in detent will push through the piston 4, the passage 6 of the stud 5 and the lunula 8 in the chamber 9; then it will be discharged by the action of the spring 15.
  • the compressed liquid is hot while the liquid in the chamber 9 and the tank is not; he will therefore there must be at each cycle a small exchange of liquid heated by the compression and unheated liquid which will allow to ensure a thermal balance of the first pump 1.
  • the envelope cylindrical 23 of the tank can be provided with cooling fins.
  • the engine oil can advantageously be used as hydraulic fluid itself by directly communicating the chamber 9 with the circuit of motor oil distribution, the temperature of this oil being regulated by the appropriate engine parts.
  • the pump according to the invention can also be used to circulate under pressures the drilling muds.
  • the suction force of the second pump II which is linked to the power of the springs 15, allows a return to the initial position of the membranes 24, because of the communication with the chamber 9.
  • this liquid is gasoline intended to supply an engine
  • it can be interesting to vary the volume of gasoline pumped by the pump It for adapt it to the operating conditions of the engine.
  • the first solution consists in producing the first pump 1, in the form of a variable flow pump using a variable inclination bias 1 tray as this is achieved in some pumps produced by the plaintiff.
  • the device according to this second solution is characterized by the fact that it comprises a double pump such as that described in the patent application 96.07043, but in which each piston of the hydraulic pump is provided with means allowing all or part of the flow pumped by said piston to be canceled.
  • Figures 3 and 4 describe a double pump similar to that of Figures 1 and 2 in which the same elements bear the same references.
  • each hollow piston 4 is traversed by in part by a pipe 30.
  • the pistons 4 are carried by two supports 31 and 32 pierced with holes in which said pistons slide.
  • the orifices pierced in the support 31 are designated by the reference 33, while the orifices pierced in the support 32 constitute the cylinders 12 mentioned above.
  • the thickness of support 32 is larger than the maximum stroke of the pistons 4.
  • the space between the supports 31 and 32 constitutes an annular chamber 35.
  • each piston 4 is partially covered by a shirt 34.
  • These sliding folders are all connected to a connecting rod of control 38 so as to slide all together between two positions extremes, the first being illustrated in Figure 3, the second being illustrated in figure 4.
  • the springs 7 of FIGS. 1 and 2, whose function is to maintain the heads of the pistons resting against their sliding block 5 are replaced by a pusher 7b which acts on a collar 6 which bears on the back of each head of piston 4.
  • the pusher 7b is counterfeit by a spring 7a.
  • the pusher 7b, counteracting the collar 6 of each piston head is traversed by a duct 37 which communicates with each other the two chambers 9 and 35.
  • each volume 13 is divided into two parts 13a, 13b by a membrane 24 pushed back by a spring 15 bearing on the membrane 24 by means of a cup 20.
  • a circular plate 42 is disposed against said portion 41b and is immobilized in position relative thereto by a pin 42a.
  • This plate 42 has as many 43 holes there are bores 12 and rooms 13.
  • the chambers 13 are formed in a part 45 which is screwed to the open end of the part 40b of the housing 40.
  • a membrane 44 which has the form of a disc having the same diameter as the plate 42. The membrane 44 is pinch between the plate 42 of the end of the piece 45.
  • Each piercing 43 communicates with a bore 12 of the pump I and is in front of a volume 13.
  • each chamber 13 is associated a conduit 50 connected to a chamber 51 where the liquid arrives at pump through a pipe 52.
  • the conduit 50 is pierced through the mass of the workpiece 45 and opens at its end opposite the chamber 51 against the membrane 44.
  • the plate 42 which is interposed between the part 41, in which are formed the bores 12 of the pistons 4 and the piece 45, in which the chambers are arranged 13 comprises two housing 53 and 54 connected by a pipe 55.
  • the housing 53 is dug in the face of the part 42 which is in contact with the membrane 44; while the housing 54 is dug in the face that is in contact with the workpiece 41.
  • the housing 54 has a configuration such that it communicates with the bore 12; and the housing 53 reaches the level of the chamber 13.
  • the hydraulic pump I is a swash plate pump or bias plate and the pistons are pistons Axial.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)

Description

La présente invention est relative à une pompe susceptible de pomper et de refouler sous haute pression pratiquement n'importe quels liquides tels que : eau, essence, gazole, huiles, liquides chimiques corrosifs et boues ; mais plus particulièrement pour l'alimentation à haute pression d'injecteurs d'essence pour moteurs à combustion interne.The present invention relates to a pump capable of pumping and to repress under high pressure practically any liquid such as: water, gasoline, diesel, oils, corrosive chemical liquids and sludge; but more especially for the high pressure supply of fuel injectors for internal combustion engines.

Les pompes a basse pression pour ce genre de liquides sont connues, ce sont d'une manière générale des pompes centrifuges, à engrenages, parfois à pistons ou autres, mais avec des pompes connues, il est impossible, sinon très difficile et coûteux, d'obtenir une haute pression de refoulement (supérieure à 50 bars), parce que, dès que l'on aborde des hautes pressions, il se produit des grippages des parties mobiles et des fuites importantes, du fait de la viscosité souvent très faible des fluides pompés.Low pressure pumps for this kind of liquids are known, they are of a generally centrifugal pumps, gear pumps, sometimes piston or others, but with known pumps it's impossible if not very difficult and costly, to obtain a high discharge pressure (greater than 50 bars), because that, when high pressures are encountered, seizures of moving parts and large leaks, because of the often very low viscosity pumped fluids.

Pour éviter de tels grippages ou de telles fuites, il est connu d'employer des pompes à membrane, mais il est alors impossible d'obtenir une pression de refoulement élevée. En effet, la membrane est d'un côté entraínée par des moyens mécaniques (came, levier ou analogue) et est de l'autre soumise à la pression de refoulement : il en résulte que, dès que la pression devient élevée la membrane se détériore aux points d'applications des efforts mécaniques.To avoid such seizures or leaks, it is known to employ diaphragm pumps, but it is then impossible to obtain a pressure of high backflow. Indeed, the membrane is on one side driven by means (cam, lever or the like) and is on the other subject to the pressure of it results that, as soon as the pressure becomes high, the membrane becomes deteriorates at the points of application of the mechanical forces.

Il est également connu, pour pomper des liquides particuliers tels par exemple que des liquides corrosifs, d'associer deux pompes : une première pompe qui est une pompe hydraulique laquelle refoule et réaspire du liquide hydraulique qui anime d'un mouvement alternatif les éléments mobiles d'une deuxième pompe, cette dernière aspirant et mettant en pression le liquide à pomper. Ces éléments mobiles qui assurent la séparation physique entre le liquide hydraulique et le liquide à pomper, tout en étant animés d'un mouvement alternatif par le liquide hydraulique, sont soit des membranes déformables soit des pistons libres.It is also known, for pumping particular liquids such as for example that corrosive liquids, to associate two pumps: a first pump which is a hydraulic pump which represses and reuses hydraulic fluid that drives reciprocating the moving parts of a second pump, this last aspirant and pressurizing the liquid to be pumped. These moving parts which ensure the physical separation between the hydraulic fluid and the liquid to pump, while being reciprocated by the hydraulic fluid, are either deformable membranes or free pistons.

Les pistons libres présentent un défaut en ce qui concerne l'étanchéité, défaut qui est incontournable dans le cas où l'on doit avoir une étanchéité absolue. Si l'on met en place un joint entre le piston libre et le cylindre dans lequel il se déplace, il n'est pas possible d'obtenir une étanchéité parfaite. Si l'on supprime le joint : ou bien il y a un très fin film d'huile entre les surfaces de frottement et donc des micro-fuites : ou bien il n'y a pas de film d'huile et les surfaces en frottement vont s'échauffer. Dans le cas particulier de l'injection d'essence à haute pression aucune fuite, aussi faible soit-elle, n'est admissible et, bien évidemment, tout échauffement risque de provoquer une explosion.The free pistons have a defect with regard to the sealing, a defect which is essential in the case where one must have an absolute seal. If we put in place a seal between the free piston and the cylinder in which it moves, it is not possible to obtain a perfect seal. If we remove the seal: or there is has a very thin film of oil between the friction surfaces and therefore micro-leaks: or there is no oil film and the friction surfaces will heat up. In the particular case of high-pressure gasoline injection no leak, also little is it, is not admissible and, of course, any warm-up risk of cause an explosion.

Les dispositifs connus à pistons libres, tels par exemple que le brevet US 4.443.160 sont donc à proscrire.Known devices with free pistons, such as, for example, the US patent 4,443,160 are therefore to be proscribed.

La présente invention concerne donc un dispositif de pompage dans lequel les éléments mobiles, animés d'un mouvement alternatif de pompage par la pompe hydraulique et assurant une séparation totalement étanche entre le liquide hydraulique "moteur" et le liquide à pomper sont des membranes déformables.The present invention thus relates to a pumping device in which the moving elements, driven by an alternating movement of pumping by the pump hydraulic and ensuring a completely sealed separation between the liquid Hydraulic "motor" and the liquid to be pumped are deformable membranes.

D'une façon générale les pompes de ce genre à membranes déformables présentent au moins l'un, si ce n'est simultanément plusieurs, des inconvénients suivants :

  • a - si la membrane de séparation et de pompage est mécaniquement liée au piston de la pompe hydraulique, il n'y a pas équipression de chaque côté de la membrane souple et cette dernière ne tient pas dans le temps, elle se détériore ;
  • b - si la membrane est complètement libre, c'est-à-dire n'est liée à aucun mécanisme d'entraínement et est mue uniquement par le liquide hydraulique refoulé par la pompe, il y a équipression entre les deux côtés de la membrane. Cependant, du fait des inévitables fuites, même très minimes, le volume de liquide hydraulique refoulé augmente à chaque cycle et finit par devenir plus important que celui que peut refouler la membrane : il se produit alors un blocage hydraulique créant une surpression telle que l'une ou l'autre des deux pompes se brise. Dans le cas particulier de l'injection d'essence à haute pression, si c'est l'élément qui refoule l'essence à haute pression qui se brise, l'incendie est inévitable :
  • c - dans un cas comme dans l'autre, c'est-à-dire que la membrane soit liée au piston ou bien libre, si le volume de liquide hydraulique qui est continuellement refoulé et réaspiré est toujours le même, il va s'échauffer du fait des cycles de compressions indéfiniment répétés, jusqu'à atteindre une température telle que la, ou les, membranes seront détruites.
    • Generally speaking, pumps of this type with deformable membranes have at least one, if not more than one, of the following disadvantages:
  • a - if the separation and pumping membrane is mechanically connected to the piston of the hydraulic pump, there is no equipressure on each side of the flexible membrane and the latter does not hold in time, it deteriorates;
  • b - if the membrane is completely free, that is to say is not linked to any drive mechanism and is moved solely by the hydraulic fluid discharged by the pump, there is equipression between the two sides of the membrane . However, because of the inevitable leaks, even very minimal, the volume of hydraulic fluid discharged increases with each cycle and ends up becoming larger than that which can push back the membrane: there then occurs a hydraulic blockage creating an overpressure such that the either one of the two pumps breaks. In the particular case of the injection of high-pressure gasoline, if it is the element that delivers high-pressure gasoline that breaks, the fire is inevitable:
  • c - in one case as in the other, that is to say that the membrane is connected to the piston or free, if the volume of hydraulic fluid which is continuously repressed and re-aspirated is still the same, it will s' to heat up because of indefinitely repeated compression cycles, until reaching a temperature such that the, or the membranes will be destroyed.

    • Dans le brevet US 4.392.787 NOTTA on a décrit un ensemble comprenant une pompe hydraulique à plateau biais, chaque piston de la pompe étant associé à son extrémité à une membrane souple qui est reliée à une tige coulissant à l'intérieur du piston. Ce dispositif présente les défauts décrits ci-dessus en "a" et "c". Le volume de liquide mis continuellement sous pression est toujours le même et va donc chauffer. D'autre part les petites fuites inévitables sont compensées par admission d'huile en complément par un clapet anti-retour, mais si accidentellement une fuite importante survient, le piston vient en contact mécanique avec la membrane qui sera alors détruite.In US Pat. No. 4,392,787, a set comprising a hydraulic pump with bias plate, each piston of the pump being associated with its end to a flexible membrane that is connected to a sliding rod inside the piston. This device has the defects described above in "a" and "c". Volume of liquid continually put under pressure is always the same and so goes heat. On the other hand the small inevitable leaks are compensated by admission of oil in addition by a check valve, but if accidentally a leak important, the piston comes into mechanical contact with the membrane which will be destroyed.

    Dans le brevet US 2.960.936 DEAN, on a décrit une pompe dans laquelle une membrane complètement libre est cycliquement écrasée et relâchée par un volume hydraulique mis en oeuvre par un piston actionné par une came.. Ce dispositif présente les défauts "b" et "c". Si il se produit, pour une raison quelconque un arrêt ou même un freinage de l'alimentation, la membrane ne va pas se redéployer complètement et une quantité correspondante de liquide hydraulique va être introduite à chaque cycle et cela jusqu'à rupture (inconvénient "b"). d'autre part, comme c'est toujours le même volume de liquide hydraulique qui est comprimé, l'échauffement est inévitable (inconvénient "c").In US Pat. No. 2,960,936 DEAN, a pump has been described in which a completely free membrane is cyclically crushed and released by a volume hydraulic operated by a piston actuated by a cam .. This device has defects "b" and "c". If it happens, for some reason a stop or even a braking of the power supply, the membrane will not redeploy completely and a corresponding amount of hydraulic fluid is going to be introduced at each cycle and this until rupture (disadvantage "b"). on the other hand, as it is always the same volume of hydraulic fluid that is compressed, warm-up is inevitable (inconvenience "c").

    Dans le brevet allemand 2.447.741 WANNER, on a décrit une pompe à membrane qui est mécaniquement liée à un piston lequel coulisse à l'intérieur d'un piston de pompe hydraulique. Les inconvénients sont les mêmes que pour le brevet US 4.392.787 cité plus haut.In German Patent 2,447,741 WANNER, a diaphragm pump has been described. which is mechanically linked to a piston which slides inside a piston of hydraulic pump. The disadvantages are the same as for the patent US 4,392,787 cited above.

    Pour éliminer ces inconvénients, la présente invention propose un dispositif dans lequel chaque membrane est libre et dans lequel, à la fin de chaque cycle d'un piston, la chambre morte, située en aval du point mort haut de ce piston (position de compression maximum), dans laquelle se trouve le liquide en contact avec la membrane est mise en communication avec la réserve de liquide hydraulique ; de sorte que le liquide qui s'y trouve est refoulé vers cette réserve d'abord par la détente du liquide, puis par effet de refoulement par la membrane qui est contretenue par un ressort.To eliminate these disadvantages, the present invention proposes a device in which which each membrane is free and in which, at the end of each cycle of a piston, the dead chamber, located downstream of the top dead center of this piston (position maximum compression), in which is the liquid in contact with the membrane is put into communication with the reserve of hydraulic fluid; of so that the liquid which is there is pushed back towards this reserve first by the relaxation of the liquid, then by the effect of repression by the membrane which is contretenue by a spring.

    On obtient ainsi, d'une part, un échange thermique continuellement répété entre le liquide comprimé et celui qui ne l'est pas et, d'autre part, une remise en position initiale de la membrane à chaque cycle ou, en d'autres termes, une élimination de toute augmentation de volume de liquide hydraulique, agissant sur la membrane, augmentation qui est inévitablement provoquée de façon permanente par les fuites ; car il n'est pas possible de réaliser une pompe hydraulique à haute pression avec des pistons, qui ne chauffe pas et qui ait un bon rendement, sans fuites.Thus, on the one hand, a heat exchange is continuously repeated between the compressed liquid and that which is not, and on the other hand, initial membrane at each cycle or, in other words, an elimination of any increase in the volume of hydraulic fluid acting on the membrane, increase which is inevitably caused permanently by the leaks; because it is not possible to realize a high pressure hydraulic pump with pistons, which does not heat and which has a good performance, without leaks.

    Selon un premier objet, la présente invention concerne une pompe permettant de pomper n'importe quelle sorte de liquide tout en lui imprimant une pression de refoulement très élevée, du type constituée par l'association de deux pompes : d'une part, une pompe hydraulique ; d'autre part, une deuxième pompe dont les moyens mobiles, réalisant l'aspiration et le refoulement du liquide à pomper, sont des membranes souples animées d'un mouvement alternatif dans un sens plus dans l'autre par le déplacement du liquide hydraulique pompé puis réaspiré par la première pompe caractérisé par le fait que les pistons de la première pompe sont creux et traversés par le liquide hydraulique qui, lors de la phase d'aspiration traverse une lunule ou rainure creusée dans la face du plateau biais ou came ; les membranes déformables étant contretenues chacune par un ressort de telle sorte qu'à la fin de la course de compression de chaque piston, la communication est établie entre la chambre où le liquide hydraulique se trouve refoulé contre la membrane et la chambre d'aspiration, ce liquide étant, d'une part, aspiré par le mouvement du piston et refoulé par la membrane sous l'action de son ressort, ce qui assure : d'une part un échange entre le liquide hydraulique chauffé par la compression et le liquide non chauffé et, d'autre part, un retour en position initiale de la membrane.According to a first object, the present invention relates to a pump for pump any kind of liquid while printing a pressure of very high discharge, of the type constituted by the association of two pumps: on the one hand, a hydraulic pump; on the other hand, a second pump whose moving means, carrying out the suction and the delivery of the liquid to be pumped, are flexible membranes animated with a reciprocating motion in a more direction in the other by the displacement of the hydraulic fluid pumped and then sucked by the first pump characterized by the fact that the pistons of the first pump are hollow and traversed by the hydraulic fluid which, during the suction phase crosses a lunula or groove dug in the face of the bias or cam plate; the deformable membranes being each controlled by a spring so that that at the end of the compression stroke of each piston, the communication is between the chamber where the hydraulic fluid is pushed back against the membrane and the suction chamber, this liquid being, on the one hand, sucked by the movement of the piston and pushed back by the membrane under the action of its spring, this which ensures: on the one hand an exchange between the hydraulic fluid heated by the compression and the unheated liquid and, on the other hand, a return to the initial position of the membrane.

    La pompe selon l'invention peut également comporter l'une ou l'autre des dispositions suivantes :

  • a - la deuxième pompe comporte autant de volumes ou alésages que la première pompe comporte d'alésages, chaque alésage de la deuxième pompe communiquant directement avec l'alésage correspondant de la première pompe de sorte que chaque piston de la première pompe refoule et aspire cycliquement le liquide hydraulique dans l'alésage correspondant de la deuxième pompe.
  • b - chaque alésage de la deuxième pompe est divisé en deux parties par une membrane déformable contretenue par un ressort, la partie communiquant avec l'alésage correspondant de la première pompe et recevant le liquide hydraulique refoulé et réaspiré par celle-ci, l'autre partie, munie de clapets d'aspiration et de refoulement, aspirant et refoulant le produit à pomper.
  • c - la chambre dans laquelle se débattent les têtes des pistons est reliée à un réservoir de liquide hydraulique.
  • d - le réservoir de liquide hydraulique est extérieur à la première pompe et communique avec cette dernière par une canalisation débouchant dans la chambre.
  • e - la pompe selon l'invention est destinée à l'alimentation sous haute pression d'injecteurs de carburant pour moteurs à combustion interne, le liquide hydraulique de la première pompe (I) pouvant être l'huile dudit moteur.
    • The pump according to the invention may also include one or other of the following provisions:
  • a - the second pump comprises as many volumes or bores as the first pump comprises bores, each bore of the second pump communicating directly with the corresponding bore of the first pump so that each piston of the first pump discharges and cyclically sucks the hydraulic fluid in the corresponding bore of the second pump.
  • b - each bore of the second pump is divided into two parts by a deformable diaphragm controlled by a spring, the part communicating with the corresponding bore of the first pump and receiving the hydraulic fluid discharged and sucked by it, the other part, equipped with suction and discharge valves, sucking and driving back the product to be pumped.
  • c - the chamber in which the heads of the pistons are struggling is connected to a reservoir of hydraulic fluid.
  • d - the hydraulic fluid reservoir is external to the first pump and communicates with the latter by a pipe opening into the chamber.
  • e - the pump according to the invention is intended for the high pressure supply of fuel injectors for internal combustion engines, the hydraulic fluid of the first pump (I) being the oil of said engine.

    • Selon un deuxième objet, la présente invention concerne des moyens permettant de faire varier la cylindrée de la première pompe et donc le débit d'essence vers les dispositifs d'injection.According to a second subject, the present invention relates to means for vary the displacement of the first pump and therefore the flow of gasoline to the injection devices.

    Ces moyens sont : soit la disposition d'un plateau biais à inclinaison variable, soit la disposition de moyens dans les pistons de la pompe hydraulique, ayant pour fonction de court-circuiter tout ou partie du volume de liquide hydraulique introduit dans l'alésage lors de la phase d'aspiration.These means are: either the provision of a variable inclination bias tray, or the arrangement of means in the pistons of the hydraulic pump, having for function to short-circuit all or part of the volume of hydraulic fluid introduced into the bore during the suction phase.

    Selon l'invention, chaque piston creux de la pompe hydraulique est muni d'ouvertures pouvant être occultées en tout ou en partie par une chemise mobile, toutes les chemises mobiles étant déplacées ensemble par un organe de commande asservi aux conditions de fonctionnement du moteur.According to the invention, each hollow piston of the hydraulic pump is provided with openings that can be obscured in whole or in part by a mobile shirt, all the moving jackets being moved together by a control member subject to the operating conditions of the engine.

    Ce dispositif peut, en outre, comporter l'une ou l'autre des dispositions suivantes :

  • a - les pistons coulissent dans deux supports percés d'orifices, ces deux supports étant séparés l'un de l'autre par un espace annulaire, constituant une chambre, dans laquelle se déplacent les chemises entre deux positions extrêmes, l'une pour laquelle les orifices n'étant pas masqués par les chemises la totalité du liquide refoulé par chaque piston reflue dans la chambre annulaire par les orifices des pistons le débit de la pompe (I) étant nul : l'autre pour laquelle tous les orifices étant masqués par les chemises chaque piston refoule la totalité du liquide hydraulique aspiré, le débit de la pompe étant alors maximum.
  • b - les chemises peuvent occuper toutes les positions intermédiaires comprises entre les deux positions extrêmes ; de sorte que le débit de la pompe (I) peut être régulé pour toutes les valeurs comprises entre un débit nul et un débit maximum.
  • c - les chemises sont attelées à un organe de commande commun lequel est asservi à tout dispositif de commande approprié pour réguler le débit d'essence à haute pression en fonction des besoins en alimentation du moteur sans que de l'essence à haute pression ne soit retournée au réservoir.
  • d - un dispositif amortisseur peut être disposé en aval de la sortie de la deuxième pompe (II) et en amont des injections pour annuler l'effet de pulsation provoqué par la première pompe (I).
  • e - le dispositif amortisseur peut être une capacité de volume important par rapport au débit d'essence, maintenu sous la pression d'injection par tout moyen approprié et se comporter sensiblement comme un accumulateur hydromécanique.
    • This device may, in addition, include one or other of the following provisions:
  • a - the pistons slide in two brackets drilled with orifices, these two supports being separated from each other by an annular space, constituting a chamber, in which the shirts move between two extreme positions, one for which the orifices not being masked by the jackets all of the liquid discharged by each piston flows back into the annular chamber through the orifices of the pistons the flow rate of the pump (I) being zero: the other for which all the orifices are masked by the jackets each piston represses all the hydraulic fluid sucked up, the flow rate of the pump then being maximum.
  • b - the shirts can occupy all the intermediate positions between the two extreme positions; so that the flow rate of the pump (I) can be regulated for all values between zero flow and maximum flow.
  • c - the jackets are coupled to a common control member which is controlled by any appropriate control device to regulate the flow of high pressure gasoline according to the engine power requirements without high pressure gasoline is returned to the tank.
  • d - a damping device may be disposed downstream of the outlet of the second pump (II) and upstream of the injections to cancel the pulsation effect caused by the first pump (I).
  • e - the damping device can be a large volume capacity with respect to the gasoline flow, maintained under the injection pressure by any appropriate means and behave substantially as a hydromechanical accumulator.

    • A titre d'exemples non limitatifs et pour faciliter la compréhension de l'invention, on a représenté aux dessins annexés :

    • Figure 1, une vue en coupe longitudinale d'un premier mode de réalisation de l'invention.
    • Figure 2, une vue en coupe transversale selon A-A de la figure 1.
    • Figure 3, une vue en coupe longitudinale de la pompe double à débit variable, les pièces étant dans la position pour laquelle le débit est maximum.
    • Figure 4, une vue de la pompe double de la figure 3, les pièces étant dans la position pour laquelle le débit est nul.
    • Figure 5, une vue selon A-A de la face du plateau biais des figures 3 et 4.
    • Figure 6, une vue en coupe longitudinale de la pompe de la figure 1 dans laquelle les membranes individuelles ont été remplacées par une membrane unique.
    • Fifure 7, une vue en coupe selon A-A de la figure 6.
    • Figure 8, une vue en coupe selon B-B de la figure 6.
    • Figure 9, une vue de détail à échelle agrandie en coupe longitudinale, d'une variante de réalisation de la pompe selon l'invention dans laquelle les clapets d'aspiration ont été supprimés.
    • Figure 10, une vue en coupe longitudinale de la pompe de la figure 6 munie du système d'aspiration par la membrane de la figure 9.
    • Figure 11, une vue d'une variante de réalisation dans laquelle la pompe hydraulique est une pompe radiale.
    As non-limiting examples and to facilitate the understanding of the invention, there is shown in the accompanying drawings:
    • Figure 1 is a longitudinal sectional view of a first embodiment of the invention.
    • Figure 2 is a cross-sectional view along AA of Figure 1.
    • Figure 3 is a longitudinal sectional view of the dual pump variable flow, the parts being in the position for which the flow is maximum.
    • Figure 4 is a view of the double pump of Figure 3, the parts being in the position for which the flow is zero.
    • Figure 5 is a view along AA of the face of the bias plate of Figures 3 and 4.
    • Figure 6 is a longitudinal sectional view of the pump of Figure 1 in which the individual membranes have been replaced by a single membrane.
    • Fifure 7, a sectional view along AA of FIG.
    • Figure 8, a sectional view along BB of Figure 6.
    • Figure 9 is an enlarged detail view in longitudinal section, of an alternative embodiment of the pump according to the invention in which the suction valves have been removed.
    • 10, a longitudinal sectional view of the pump of FIG. 6 provided with the suction system by the membrane of FIG. 9.
    • Figure 11 is a view of an alternative embodiment in which the hydraulic pump is a radial pump.

    En se reportant aux figures 1 et 2 on voit que le dispositif selon l'invention comporte une première pompe, désignée par la référence générale I et une deuxième pompe, désignée par la référence générale II.Referring to FIGS. 1 and 2, it can be seen that the device according to the invention comprises a first pump, designated by the general reference I and a second pump, designated by the general reference II.

    La première pompe I est une pompe à pistons axiaux animés d'un mouvement alternatif de va-et-vient par un plateau biais 1.The first pump I is an axial piston pump driven by a movement alternate back-and-forth by a bias tray 1.

    Le plateau biais 1 est solidaire d'un arbre moteur 2 (entraíné par tout moyen non représenté) porté par des roulements 3. Une pluralité de pistons creux 4 prennent appui contre la face oblique du plateau 1 chacun au moyen d'un plot de glissement 5, qui est percé en son centre d'un alésage 6. Chaque piston 4 est maintenu par un ressort 7 contre son plot. Sur la face avant 1 est gravée une lunule 8. Lorsque l'arbre 2 est entraíné en rotation, le plateau biais 1, les plots 5 et les têtes sphériques 4a des pistons 4 se débattent dans une chambre 9. Cette chambre 9 débouche, par une pluralité de perçages 22, traversant le corps 21 de la pompe 1, dans un réservoir 11. Ce réservoir 11 est constitué par une enveloppe cylindrique 23 qui entoure le corps 21.The bias plate 1 is integral with a drive shaft 2 (driven by any means not shown) carried by bearings 3. A plurality of hollow pistons 4 take support against the oblique face of the plate 1 each by means of a sliding block 5, which is pierced at its center with a bore 6. Each piston 4 is held by a spring 7 against his stud. On the front face 1 is engraved a lunula 8. When the shaft 2 is rotated, the bias plate 1, the studs 5 and the heads spherical 4a pistons 4 are struggling in a room 9. This room 9 opens, through a plurality of holes 22, through the body 21 of the pump 1, in a tank 11. This tank 11 is constituted by a cylindrical envelope 23 surrounding the body 21.

    Lorsque l'arbre moteur 2 tourne, la face du plateau biais 1 oscille dans la chambre 9 de sorte que les pistons 4 sont animés d'un mouvement alternatif de va-et-vient : dans le sens qui correspond à l'aspiration, les pistons 4 sont mus par leur ressort 7 ; dans l'autre sens qui correspond au refoulement sous pression, ils sont repoussés à l'encontre du ressort 7 par le plateau biais 1. Lors de la phase d'aspiration, le liquide hydraulique qui se trouve dans la chambre 9 pénètre à l'intérieur des pistons 4 en passant par la lunule 8 et l'alésage 6 des plots 5.When the motor shaft 2 rotates, the side of the bias plate 1 oscillates in the chamber 9 so that the pistons 4 are driven reciprocating back and forth: in the direction corresponding to the suction, the pistons 4 are driven by their spring 7; in the other direction which corresponds to the repression under pressure, they are pushed back to against the spring 7 by the bias plate 1. During the suction phase, the hydraulic fluid that is in the chamber 9 gets inside the pistons 4 passing through the lunula 8 and the bore 6 of the studs 5.

    Ce type de pompe est connu et décrit dans de nombreux brevets antérieurs appartenant à la demanderesse. This type of pump is known and described in many prior patents owned by the plaintiff.

    Lorsque la pompe hydraulique I est employée de façon connue, chaque alésage 12 dans lequel coulisse un piston creux 4 comporte à son extrémité un clapet anti-retour ; de sorte que l'ensemble desdits pistons 4 provoque un débit sous pression (et même sous haute pression puisque l'on peut dépasser 1000 bars avec ce type de pompe).When the hydraulic pump I is used in known manner, each bore 12 in which slides a hollow piston 4 has at its end a non-return valve ; so that all of said pistons 4 causes a flow under pressure (and even under high pressure since one can exceed 1000 bars with this type of pump).

    Cependant, dans le cadre de la présente invention aucun des alésages 12 dans lesquels coulissent les pistons 4 ne comporte de clapet anti-retour.However, in the context of the present invention, none of the bores 12 in which slide the pistons 4 has a non-return valve.

    Une pompe 1 est associée à la pompe I immédiatement en aval de celle-ci.A pump 1 is associated with the pump I immediately downstream thereof.

    A chaque alésagel2 de la pompe I, dans lequel coulisse un piston 4, correspond, dans la pompe II, une chambre ou alésage 13 divisé en deux parties 13a et 13b par une membrane souple 24 contretenue par un ressort 15. La partie 13a communique directement avec l'extrémité de l'alésage 12, tandis que la partie 13b est munie à son extrémité opposée à la membrane 24 d'un clapet d'aspiration 16 et d'un clapet de refoulement 17. Tous les clapets 17 débitent dans une canalisation commune 18.With each bore 2 of the pump I, in which slides a piston 4, corresponds, in the pump II, a chamber or bore 13 divided into two parts 13a and 13b by a flexible membrane 24 biased by a spring 15. The part 13a communicates directly with the end of the bore 12, while the portion 13b is provided with its end opposite the membrane 24 of a suction valve 16 and a valve 17. All valves 17 flow in a common pipe 18.

    De préférence, comme cela est représenté, chaque ressort 15 prend appui sur la face arrière de la membrane 24 par l'intermédiaire d'une coupelle 20. La forme de la coupelle 20 est déterminée de façon à ce que l'appui de la coupelle 20 sur la face arrière de la membrane 24 ne provoque aucune détérioration de celle-ci.Preferably, as shown, each spring 15 is supported on the rear face of the membrane 24 via a cup 20. The shape of the cup 20 is determined so that the support of the cup 20 on the face rear of the membrane 24 does not cause any deterioration thereof.

    Le fonctionnement est décrit ci-après :The operation is described below:

    Lorsque l'arbre moteur 2 est entraíné, les pistons 4 refoulent le liquide hydraulique dans les chambres 13. Le liquide hydraulique refoulé dans la partie 13a de la chambre 13, prend appui sur la face avant de la membrane 24 et provoque un déplacement de celle-ci, dans le sens de la flèche f1 (fig.1). En se déplaçant cette membrane 24 refoule le liquide contenu dans la partie 13b de la chambre 13. Ce refoulement se fait à travers le clapet anti-retour 17.When the driving shaft 2 is driven, the pistons 4 repress the hydraulic fluid 13. The hydraulic fluid discharged into part 13a of the chamber 13, bears on the front face of the membrane 24 and causes a move it in the direction of the arrow f1 (fig.1). In moving this membrane 24 delivers the liquid contained in the portion 13b of the chamber 13. This backflow is through the non-return valve 17.

    Puis, lorsque le plateau biais 1 continue à tourner, le plot 5 de chaque piston 4 passe sur la lunule 8 ce qui met la chambre 13a, l'intérieur du piston creux 4 et la chambre d'aspiration 9 en communication. Au tout début de la course du plot 5 sur la lunule 8 le liquide sous haute pression qui est dans la chambre 13a se détend en direction de la chambre 9 ; ensuite sous l'action du ressort 7 du piston 4 et du ressort 15 de la membrane 24 le liquide se trouvant dans la chambre 13a est refoulé dans l'alésage 12 et de là vers la chambre 9.Then, when the bias plate 1 continues to rotate, the stud 5 of each piston 4 passes on the lunula 8 which puts the chamber 13a, the interior of the hollow piston 4 and the suction chamber 9 in communication. At the very beginning of the plot race 5 on the lunula 8 the high pressure liquid that is in the chamber 13a relaxes in direction of the chamber 9; then under the action of the spring 7 of the piston 4 and the spring 15 of the membrane 24 the liquid in the chamber 13a is pushed back into the bore 12 and from there to the chamber 9.

    Ainsi le liquide hydraulique, qui se trouve dans la chambre morte à l'extrémité de chaque alésage 12 lorsque le piston 4 est à l'extrémité de sa course de compression et dans la chambre 13a, est renouvelé à la fin de chaque cycle de compression, ce qui évite tout échauffement de ce liquide, ce qui serait inévitable autrement. De plus, cette remise en communication directe entre la chambre 13a et la chambre 9, et cela à chaque cycle, réalise une remise en position initiale des éléments mobiles de sorte que le volume de liquide hydraulique refoulé dans la chambre 13a demeure rigoureusement égal à lui-même, les inévitables fuites de la pompe hydraulique étant renvoyées dans la chambre 9. Cette mise en communication des chambres 9 et 13a supprime donc les inconvénients décrits précédemment en "b" et "c".So the hydraulic fluid, which is in the dead chamber at the end of each bore 12 when the piston 4 is at the end of its compression stroke and in the chamber 13a, is renewed at the end of each compression cycle, this which avoids any heating up of this liquid, which would be inevitable otherwise. Of moreover, this handing over of direct communication between the chamber 13a and the chamber 9, and this at each cycle, realizes a reset to the initial position of the moving elements so that the volume of hydraulic fluid discharged into the chamber 13a remains strictly equal to itself, the inevitable leaks from the pump hydraulics being returned to chamber 9. This communication between chambers 9 and 13a thus eliminates the disadvantages described previously in "b" and "c".

    Le déplacement de la membrane 24 dans le sens de la flèche f2 a pour effet d'aspirer le produit à pomper dans la partie 13b de l'alésage 13, à travers le clapet d'admission anti-retour 16 et de refouler le liquide hydraulique se trouvant dans la partie 13a.The displacement of the membrane 24 in the direction of the arrow f2 has the effect to suck the product to be pumped into the part 13b of the bore 13, through the valve anti-return valve 16 and to discharge the hydraulic fluid in the part 13a.

    Ainsi le produit à pomper est alternativement aspiré puis refoulé par le mouvement alternatif des membranes 24, ce mouvement étant provoqué par les variations du volume occupé par le liquide hydraulique dans les parties 13a des alésages 13, ces variations de volume étant provoquées par les alternances de refoulement et d'aspiration du liquide hydraulique par les pistons 4 de la première pompe I.Thus the product to be pumped is alternately sucked and then pushed back by the movement membrane 24, this movement being caused by the variations of the volume occupied by the hydraulic fluid in the parts 13a of the bores 13, these variations in volume being caused by alternations of suction of the hydraulic fluid by the pistons 4 of the first pump I.

    Chaque membrane 24 est soumise, sur ses deux faces avant et arrière et cela de façon uniformément répartie sur toute la surface de la membrane, à la même pression : d'un côté la pression du liquide hydraulique moteur, de l'autre la pression du liquide refoulé. La membrane ne subit donc aucun effort mécanique et ne peut donc pas se déchirer.Each membrane 24 is subjected on its two front and rear faces and that of uniformly distributed over the entire surface of the membrane, at the same pressure: on one side the pressure of the engine hydraulic fluid, on the other hand the pressure of the liquid discharged. The membrane therefore undergoes no mechanical effort and therefore can not tear.

    La pompe selon la présente invention est donc une pompe à membranes dans laquelle chaque membrane est, en phase de refoulement, une équipression de chaque côté ce qui permet d'avoir une pression de refoulement égale à la pression hydraulique que peut fournir la première pompe I. The pump according to the present invention is therefore a diaphragm pump in which each membrane is, in the phase of repression, an equipression of each side which allows to have a pressure of discharge equal to the pressure hydraulic that can provide the first pump I.

    La pompe selon la présente invention peut être employée, entre autres, pour mettre en pression des liquides n'ayant aucun pouvoir graissant. En particulier elle peut être employée pour alimenter des injecteurs de moteur à combustion interne (moteurs de voitures automobiles) alimentés en super-carburant et/ou en GPL liquide en tant que carburant de substitution par exemple. Le super-carburant est aspiré par les clapets 16, refoulé sous haute pression (plus de 50 bars) par les clapets 17 sans que le carburant ne soit jamais mis en contact avec des organes métalliques devant glisser les uns contre les autres.The pump according to the present invention can be used, inter alia, to in pressure of liquids having no grinding power. In particular she can be used to supply internal combustion engine injectors (motor vehicle engines) powered by super-fuel and / or LPG liquid as a substitute fuel for example. The super-fuel is aspirated by the valves 16, discharged under high pressure (more than 50 bar) by the valves 17 without the fuel ever being in contact with organs metal to slide against each other.

    Il est à noter qu'à des pressions élevées on ne peut plus considérer les liquides comme incompressibles. Lorsque un piston 4 est en bout de course de refoulement, la pression du liquide hydraulique est à son maximum. Comme cela a été dit plus haut, lorsque le plot 5 se trouve sur le début de la lunule 8 le liquide, en se détendant va refouler à travers le piston 4, le passage 6 du plot 5 et la lunule 8 dans la chambre 9 ; puis il sera refoulé par l'action du ressort 15. Le liquide comprimé est chaud alors que le liquide dans la chambre 9 et le réservoir ne l'est pas ; il va donc y avoir à chaque cycle un petit échange de liquide chauffé par la compression et de liquide non chauffé ce qui va permettre d'assurer un équilibre thermique de la première pompe 1. De préférence, bien que cela ne soit pas représenté, l'enveloppe cylindrique 23 du réservoir peut être munie d'ailettes de refroidissement.It should be noted that at high pressures, liquids can no longer be considered as incompressible. When a piston 4 is at the end of the delivery stroke, the hydraulic fluid pressure is at its maximum. As has been said more high, when the stud 5 is on the beginning of the lunula 8 the liquid, in detent will push through the piston 4, the passage 6 of the stud 5 and the lunula 8 in the chamber 9; then it will be discharged by the action of the spring 15. The compressed liquid is hot while the liquid in the chamber 9 and the tank is not; he will therefore there must be at each cycle a small exchange of liquid heated by the compression and unheated liquid which will allow to ensure a thermal balance of the first pump 1. Preferably, although not shown, the envelope cylindrical 23 of the tank can be provided with cooling fins.

    Dans le cas où la pompe double selon l'invention est employée, comme indiqué plus haut, pour l'alimentation à haute pression d'injecteurs d'essence pour moteurs, on peut avantageusement employer comme liquide hydraulique l'huile du moteur lui-même en faisant communiquer directement la chambre 9 avec le circuit de distribution d'huile du moteur, la température de cette huile étant régulée par les organes appropriés du moteur.In the case where the double pump according to the invention is used, as indicated above, for the high pressure supply of fuel injectors for engines, the engine oil can advantageously be used as hydraulic fluid itself by directly communicating the chamber 9 with the circuit of motor oil distribution, the temperature of this oil being regulated by the appropriate engine parts.

    La pompe selon l'invention peut également être employée pour faire circuler sous pressions les boues de forage.The pump according to the invention can also be used to circulate under pressures the drilling muds.

    Elle peut en fait être employée pour mettre en pression n'importe quels liquides, y compris les liquides corrosifs ou agressifs.It can actually be used to pressurize any liquid, including including corrosive or aggressive liquids.

    Dans la cas où l'étage hydraulique, pompe I, est confronté à un liquide de forte viscosité, comme c'est le cas d'un usage à froid, par exemple, il est préférable, comme cela est connu, de disposer des moyens mécaniques maintenant les têtes 4a de pistons 4 sur leurs plots 5 pendant la phase d'aspiration.In the case where the hydraulic stage, pump I, is confronted with a liquid of strong viscosity, as is the case with cold use, for example, it is preferable, as is known, to have mechanical means now heads 4a of pistons 4 on their pads 5 during the suction phase.

    Comme expliqué précédemment, l'effort d'aspiration de la deuxième pompe II, qui est lié à la puissance des ressorts 15, permet un retour en position initiale des membranes 24, du fait de la communication avec la chambre 9.As explained above, the suction force of the second pump II, which is linked to the power of the springs 15, allows a return to the initial position of the membranes 24, because of the communication with the chamber 9.

    Si il n'y avait pas cette remise en position initiale, permise par cette communication avec la réserve de liquide hydraulique, il risquerait de se produire une légère dérive à chaque tour de la pompe.If there was not this reset to the original position, allowed by this communication with the reserve of hydraulic fluid, it might occur a slight drift every turn of the pump.

    Cette dérive provoquerait rapidement un différentiel de volumes entre l'alésage 12 et la partie 13a de l'alésage 13 correspondant, ce qui à son tour, provoquerait rapidement une mise en butée des membranes 24 et, immédiatement, une rupture de la pompe (soit au niveau de la pompe I, soit au niveau de la pompe II).This drift would quickly cause a volume differential between the bore 12 and the portion 13a of the corresponding bore 13, which in turn would cause quickly an abutment of the membranes 24 and, immediately, a rupture pump (either at pump I or at pump II).

    Il apparaít donc bien que cette remise à zéro, ou remise en position initiale des éléments mobiles 24 de la deuxième pompe II, par l'intermédiaire de la lunule 8 est capitale.It therefore appears that this reset, or reset to initial position movable elements 24 of the second pump II, via the lunula 8 is capital city.

    Les figures 3 à 5 concernent un perfectionnement au dispositif des figures 1 et 2 au moyen duquel il va être possible de faire varier à volonté le débit du liquide à pomper.Figures 3 to 5 relate to an improvement to the device of Figures 1 and 2 to by means of which it will be possible to vary at will the flow of the liquid to pump.

    Lorsque ce liquide est de l'essence destinée à alimenter un moteur, il peut être intéressant de faire varier le volume d'essence pompé par la pompe Il pour l'adapter aux conditions de fonctionnement du moteur.When this liquid is gasoline intended to supply an engine, it can be interesting to vary the volume of gasoline pumped by the pump It for adapt it to the operating conditions of the engine.

    Il faut pour qu'un moteur puisse tourner à plein régime, déterminer la cylindrée de la pompe en fonction des conditions extrêmes d'utilisation du moteur, à savoir : fonctionnement à régime maximum et pleine charge. Cela définit donc un débit maximum de la pompe lequel est fourni en permanence ; de sorte que, en dehors de ces conditions extrêmes d'utilisation, la pompe fournit un débit excédentaire, qui est retourné au réservoir.It takes a motor to run at full speed, determine the displacement of the pump according to the extreme conditions of use of the engine, namely: operating at maximum speed and full load. This therefore defines a debit maximum of the pump which is permanently supplied; so that, apart these extreme conditions of use, the pump provides excess flow, who returned to the tank.

    Mais l'essence ainsi ramenée au réservoir se trouve avoir été échauffée par la compression, de sorte que de l'essence chaude est ramenée en permanence au réservoir. Au fur et à mesure que le réservoir se vide, l'essence devient de plus en plus chaude de sorte qu'il risque d'apparaítre dans le réservoir des vapeurs d'essence indésirables dont le traitement est rendu difficile par des normes de plus en plus sévères en particulier en ce qui concerne les moteurs à essence à injection directe.But the essence thus brought back to the tank is to have been heated by the compression, so that hot gasoline is brought back permanently to tank. As the tank empties, gasoline becomes more and more warmer so it may appear in the vapor tank of undesirable gasoline whose treatment is made difficult by standards of more more severe especially with regard to gasoline injection engines direct.

    Il s'avère donc nécessaire de moduler le débit de la pompe en fonction des exigences du moteur.It is therefore necessary to modulate the flow of the pump according to the engine requirements.

    La première solution consiste à réaliser la première pompe 1, sous la forme d'une pompe à débit variable en utilisant un plateau biais 1 à inclinaison variable comme cela est réalisé dans certaines pompes produites par la demanderesse.The first solution consists in producing the first pump 1, in the form of a variable flow pump using a variable inclination bias 1 tray as this is achieved in some pumps produced by the plaintiff.

    Mais une telle pompe risque d'être trop onéreuse pour la production automobile en grande série ; de sorte qu'une deuxième solution est décrite ci-après.But such a pump may be too expensive for automotive production in large series; so that a second solution is described below.

    Le dispositif selon cette deuxième solution est caractérisé par le fait qu'il comporte une pompe double telle que celle décrite dans la demande de brevet 96.07043, mais dans laquelle chaque piston de la pompe hydraulique est muni de moyens permettant d'annuler en tout ou partie le débit pompé par ledit piston.The device according to this second solution is characterized by the fact that it comprises a double pump such as that described in the patent application 96.07043, but in which each piston of the hydraulic pump is provided with means allowing all or part of the flow pumped by said piston to be canceled.

    Les figures 3 et 4 décrivent une pompe double analogue à celle des figures 1 et 2 dans laquelle les mêmes éléments portent les mêmes références.Figures 3 and 4 describe a double pump similar to that of Figures 1 and 2 in which the same elements bear the same references.

    En se reportant à ces figures, on voit que chaque piston creux 4 est traversé de part en part par une canalisation 30.Referring to these figures, it can be seen that each hollow piston 4 is traversed by in part by a pipe 30.

    D'autre part, les pistons 4 sont portés par deux supports 31 et 32 percés d'orifices dans lesquels coulissent lesdits pistons. Les orifices percés dans le support 31 sont désignés par la référence 33, tandis que les orifices percés dans le support 32 constituent les cylindres 12 mentionnés plus haut. Dans ce but, l'épaisseur du support 32 est plus grande que la course maxima des pistons 4.On the other hand, the pistons 4 are carried by two supports 31 and 32 pierced with holes in which said pistons slide. The orifices pierced in the support 31 are designated by the reference 33, while the orifices pierced in the support 32 constitute the cylinders 12 mentioned above. For this purpose, the thickness of support 32 is larger than the maximum stroke of the pistons 4.

    L'espace compris entre les supports 31 et 32 constitue une chambre annulaire 35.The space between the supports 31 and 32 constitutes an annular chamber 35.

    Dans cet espace 35 chaque piston 4 est partiellement recouvert par une chemise coulissante 34. Ces chemises coulissantes sont toutes reliées à une bielle de commande 38 de façon à pouvoir coulisser toutes ensemble entre deux positions extrêmes, la première étant illustrée à la figure 3, la seconde étant illustrée à la figure 4. In this space 35 each piston 4 is partially covered by a shirt 34. These sliding folders are all connected to a connecting rod of control 38 so as to slide all together between two positions extremes, the first being illustrated in Figure 3, the second being illustrated in figure 4.

    Dans la position représentée à la figure 3, lesdites chemises 34 occultent les perçages 36 qui font communiquer la canalisation interne 30 de chaque piston 4 avec la chambre annulaire 35.Dans la position représentée à la figure 4, les chemises 34 découvrent lesdits perçages 36.In the position shown in FIG. 3, said shirts 34 obscure the holes 36 which communicate the internal pipe 30 of each piston 4 with the annular chamber 35.In the position shown in FIG. shirts 34 discover said holes 36.

    Les ressorts 7 des figures 1 et 2, qui ont pour fonction de maintenir les têtes des pistons en appui contre leur plot de glissement 5 sont remplacés par un poussoir 7b qui agit sur une collerette 6 laquelle prend appui sur l'arrière de chaque tête de piston 4. Le poussoir 7b est contrefaçon par un ressort 7a.The springs 7 of FIGS. 1 and 2, whose function is to maintain the heads of the pistons resting against their sliding block 5 are replaced by a pusher 7b which acts on a collar 6 which bears on the back of each head of piston 4. The pusher 7b is counterfeit by a spring 7a.

    Le poussoir 7b, contretenant la collerette 6 de chaque tête de piston est traversé par une canalisation 37 qui fait communiquer entre elles les deux chambres 9 et 35.The pusher 7b, counteracting the collar 6 of each piston head is traversed by a duct 37 which communicates with each other the two chambers 9 and 35.

    Ainsi lorsque, sous l'effet de la bielle de commande 38, les chemises 34 sont dans la position représentée à la figure 4, le liquide hydraulique refoulé par chaque piston 4 reflue par les canalisations 30 et 36 jusque dans la chambre annulaire 35, et, de là, par le perçage 37, dans la chambre 9. Il en résulte que le débit de la pompe hydraulique I est nul, donc que les membranes 24 ne sont animées d'aucun mouvement et n'exercent aucune action de pompage et de refoulement sous pression d'essence vers les injecteurs : le débit d'essence vers les injecteurs est donc également nul.Thus when, under the effect of the control rod 38, the shirts 34 are in the position shown in Figure 4, the hydraulic fluid discharged by each piston 4 flows back through the pipes 30 and 36 into the annular chamber 35, and from there, through the bore 37, into the chamber 9. As a result, the flow rate of the hydraulic pump I is zero, so that the membranes 24 are not animated by any movement and do not exert any action of pumping and repression under fuel pressure to the injectors: the fuel flow to the injectors is therefore also zero.

    Lorsque, sous l'effet de la commande 38, les chemises 34 sont dans la position représentée à la figure 1, les perçages 36 sont occultés par lesdites chemises et le débit de la pompe hydraulique I est maximum. Il en résulte que le débit d'essence vers les injecteurs est également maximum.When, under the effect of the command 38, the shirts 34 are in the position shown in FIG. 1, the holes 36 are obscured by said folders and the Flow rate of hydraulic pump I is maximum. As a result, the flow of gasoline towards the injectors is also maximum.

    Entre ces deux positions extrêmes tous les débits intermédiaires peuvent être obtenus en fonction de la position des chemises 34, position déterminée par la position de la bielle 38 qui est asservie au fonctionnement du moteur par tout dispositif de contrôle approprié.Between these two extreme positions all intermediate flows can be obtained according to the position of the shirts 34, position determined by the position of the connecting rod 38 which is slaved to the operation of the engine by any appropriate control device.

    Il en résulte que le débit de sortie de la pompe Il est régulé en fonction du débit d'essence qui est nécessaire à l'injection et que les retours d'essence excédentaires au réservoir sont minorés au maximum.As a result, the output flow of the pump It is regulated according to the flow rate gasoline that is needed for fuel injection and that excess fuel returns to the tank are minimized to the maximum.

    Il est à noter toutefois que le débit d'essence ainsi obtenu est un débit pulsé. En effet, si par exemple, les chemises 34 sont en une position telle que seulement 10 % du débit maximum de la pompe I soit délivré dans la partie 13a du volume 13, cela signifie que cette pompe I ne fournit aucun débit pendant 90 % de la course de chaque piston ou encore qu'il n'y a de débit que sur 10 % de la course de chaque piston. Cela a pour effet que le débit est un débit pulsé.It should be noted, however, that the gas flow thus obtained is a pulsed flow. In effect, if for example, the shirts 34 are in a position such that only 10 % of the maximum flow rate of pump I is delivered in part 13a of volume 13, this means that this pump I provides no flow for 90% of the stroke of each piston or that there is only flow on 10% of the stroke of each piston. This has the effect that the flow is a pulsed flow.

    Il en résulte donc un inconvénient qu'il faut supprimer.This results in a disadvantage that must be removed.

    Dans ce but, on dispose en aval de la sortie 29 et en amont des injecteurs un dispositif éliminant ces pulsations. Ce dispositif peut avantageusement être constitué de façon analogue à un accumulateur hydraulique c'est-à-dire constitué par une capacité ayant un volume important par rapport au débit fourni aux injecteurs et maintenu sous pression constante.For this purpose, there is downstream of the outlet 29 and upstream of the injectors a device eliminating these pulsations. This device can advantageously be constituted in a similar manner to a hydraulic accumulator that is to say constituted capacity having a significant volume compared to the flow rate provided to the injectors and kept under constant pressure.

    On obtient ainsi un débit d'injection correspondant exactement aux besoins en essence du moteur, sans retour au réservoir, ce débit étant régulier, c'est-à-dire sans pulsions.This gives an injection flow exactly corresponding to the needs in engine fuel, without return to the tank, this flow being regular, that is to say without urges.

    La figure 6 représente une pompe analogue à la pompe de la figure 1, dans laquelle les mêmes éléments portent les mêmes références.FIG. 6 represents a pump similar to the pump of FIG. 1, in which the same elements carry the same references.

    Le réservoir 11 de la figure 1 qui enveloppe la pompe hydraulique est remplacé par un réservoir extérieur 1 1a ; pour le reste, tous les composants sont identiques à la seule exception de la membrane de la pompe Il de la figure 1.The tank 11 of FIG. 1 which surrounds the hydraulic pump is replaced by an outer tank 1 1a; for the rest, all the components are identical to the only exception of the pump diaphragm II of Figure 1.

    Dans la pompe de la figure 1, chaque volume 13 est divisé en deux parties 13a, 13b par une membrane 24 repoussée par un ressort 15 prenant appui sur la membrane 24 au moyen d'une coupelle 20.In the pump of FIG. 1, each volume 13 is divided into two parts 13a, 13b by a membrane 24 pushed back by a spring 15 bearing on the membrane 24 by means of a cup 20.

    Dans la pompe de la figure 6, les membranes individuelles 24 sont remplacées par une membrane unique 44, qui, aux endroits des chambres 13 va se déformer pour pénétrer partiellement dans ledit volume 13 à l'encontre du ressort 15 correspondant.In the pump of FIG. 6, the individual membranes 24 are replaced by a single membrane 44, which at the locations of the chambers 13 will deform to partially penetrate into said volume 13 against the spring 15 corresponding.

    De façon plus précise, la pompe de la figure 6, comme celle de la figure 1, comporte un carter de pompe monobloc 40. en deux parties cylindriques 40a, et 40b, la partie 40b ayant un diamètre interne supérieur à celui de la partie 40a. Dans la partie 40a sont disposés les roulements 3, l'arbre moteur 2, le plateau biais 1, la chambre d'alimentation 9 et la partie arrière 4 la d'une pièce 41 dans laquelle sont forés les alésages 12. La partie avant 41b de cette pièce se trouve dans la partie 40b de diamètre supérieur du carter 40 ; de sorte que cette partie avant 41b repose contre l'épaulement qui sépare les deux parties 40a et 40b du carter 40. Les alésages 12 des pistons 4 débouchent à la face avant de cette partie 41b, une plaque circulaire 42 est disposée contre ladite partie 41b et est immobilisée en position par rapport à celle-ci par un pion 42a. Cette plaque 42 comporte autant de perçages 43 qu'il y a d'alésages 12 et de chambres 13. Les chambres 13 sont ménagées dans une pièce 45 qui est vissée à l'extrémité ouverte de la partie 40b du carter 40. Entre la pièce 45 et la plaque 42 est disposée une membrane 44 qui a la forme d'un disque ayant le même diamètre que la plaque 42. La membrane 44 est pincée entre la plaque 42 de l'extrémité de la pièce 45. Chaque perçage 43 communique avec un alésage 12 de la pompe I et se trouve en face d'un volume 13.More specifically, the pump of FIG. 6, like that of FIG. comprises a one-piece pump casing 40. in two cylindrical parts 40a, and 40b, the portion 40b having an internal diameter greater than that of the portion 40a. In the part 40a are arranged the bearings 3, the motor shaft 2, the bias plate 1, the feeding chamber 9 and the rear portion 4a of a workpiece 41 in which are drilled the bores 12. The front part 41b of this part is in the part 40b of greater diameter of the casing 40; so this part before 41b rests against the shoulder which separates the two parts 40a and 40b of the housing 40. The bores 12 of the pistons 4 open to the front face of this part 41b, a circular plate 42 is disposed against said portion 41b and is immobilized in position relative thereto by a pin 42a. This plate 42 has as many 43 holes there are bores 12 and rooms 13. The chambers 13 are formed in a part 45 which is screwed to the open end of the part 40b of the housing 40. Between the piece 45 and the plate 42 is disposed a membrane 44 which has the form of a disc having the same diameter as the plate 42. The membrane 44 is pinch between the plate 42 of the end of the piece 45. Each piercing 43 communicates with a bore 12 of the pump I and is in front of a volume 13.

    Lorsqu'un piston 4 va refouler du liquide hydraulique sous haute pression, ce liquide va être refoulé hors de l'alésage 12, dans le perçage 43 et va déformer la partie de la membrane 44 qui se trouve en face de la chambre 13 correspondante, déformation qui se fait à l'encontre du ressort 15 prenant appui contre l'autre face de la membrane 44 par la coupelle 20. Le liquide à pomper se trouvant dans la chambre 13 (derrière la coupelle 20) est refoulé par le clapet anti-retour 17. Lorsque le piston 4 recule dans son alésage 12, la partie de la membrane 44 qui s'était déformée, était entrée, partiellement, dans le volume 13, est repoussée par le ressort 15 et revient à sa forme initiale en aspirant le liquide à pomper par le clapet anti-retour 16.When a piston 4 will discharge hydraulic fluid under high pressure, this liquid will be discharged out of the bore 12, in the bore 43 and will deform the part of the membrane 44 which faces the corresponding chamber 13, deformation which is against the spring 15 bearing against the other side of the membrane 44 by the cup 20. The liquid to be pumped lying in the chamber 13 (behind the cup 20) is discharged by the non-return valve 17. When the piston 4 moves back into its bore 12, the part of the membrane 44 which had distorted, had entered, partially, in volume 13, is pushed back by the spring 15 and returns to its original shape by sucking the liquid to be pumped by the valve anti-return 16.

    Comme dans les cas précédents, il y a communication directe entre le perçage 43 et la chambre 9 par la lunule 8.As in the previous cases, there is direct communication between the piercing 43 and the chamber 9 by the lunula 8.

    En se reportant à la figure 9, qui est une vue agrandie, on voit que : à chaque chambre 13 est associé un conduit 50 relié à une chambre 51 où arrive le liquide à pomper par une conduite 52. Le conduit 50 est percé à travers la masse de la pièce 45 et débouche, à son extrémité opposée à la chambre 51 contre la membrane 44. La plaque 42 qui est interposée entre la pièce 41, dans laquelle sont ménagés les alésages 12 des pistons 4 et la pièce 45, dans laquelle sont ménagées les chambres 13 comporte deux logements 53 et 54 reliés par une conduite 55. Le logement 53 est creusé dans la face de la pièce 42 qui est en contact avec la membrane 44 ; tandis que le logement 54 est creusé dans la face qui est en contact avec la pièce 41. Le logement 54 a une configuration telle qu'il communique avec l'alésage 12 ; et le logement 53 arrive jusqu'au niveau de la chambre 13.Referring to Figure 9, which is an enlarged view, we see that at each chamber 13 is associated a conduit 50 connected to a chamber 51 where the liquid arrives at pump through a pipe 52. The conduit 50 is pierced through the mass of the workpiece 45 and opens at its end opposite the chamber 51 against the membrane 44. The plate 42 which is interposed between the part 41, in which are formed the bores 12 of the pistons 4 and the piece 45, in which the chambers are arranged 13 comprises two housing 53 and 54 connected by a pipe 55. The housing 53 is dug in the face of the part 42 which is in contact with the membrane 44; while the housing 54 is dug in the face that is in contact with the workpiece 41. The housing 54 has a configuration such that it communicates with the bore 12; and the housing 53 reaches the level of the chamber 13.

    Ainsi, lorsque le liquide sous pression est refoulé par un piston 4, le liquide sous pression arrive par le logement 54 et la conduite 55 dans le logement 53 et la membrane est appliquée par la pression hydraulique contre l'orifice de la conduite 50 qui est ainsi obturé. Par contre, lorsque le piston 4 est en phase d'aspiration, le mouvement de la coupelle 20 qui repousse la membrane 44 dégage celle-ci de l'orifice de la conduite 50. La membrane 44 étant plaquée au fond du logement 53, cela dégage entre la membrane 44 et la paroi de la pièce 45 un espace 56 qui assure la communication entre la conduite 50 et la chambre 13 et permet ainsi l'admission dans cette chambre 13 du liquide à pomper.Thus, when the pressurized liquid is discharged by a piston 4, the liquid under pressure arrives through the housing 54 and the pipe 55 into the housing 53 and the membrane is applied by the hydraulic pressure against the orifice of the pipe 50 which is thus closed. On the other hand, when the piston 4 is in the suction phase, the movement of the cup 20 which pushes the membrane 44 releases it from the orifice of the pipe 50. The membrane 44 being pressed at the bottom of the housing 53, this releases between the membrane 44 and the wall of the room 45 a space 56 which ensures the communication between the pipe 50 and the chamber 13 and thus allows the admission into this chamber 13 of the liquid to be pumped.

    Il est préférable que le liquide à pomper (qui est par exemple de l'essence) arrive par le tuyau 52 à une faible pression, de l'ordre de 1 à 2 bars, donnée par une pompe électrique de type connu, de façon que, dès que la pression hydraulique disparaít dans le logement 53, la membrane 44 soit repoussée pour dégager le passage 56.It is preferable that the liquid to be pumped (which is, for example, gasoline) arrives by the pipe 52 at a low pressure, of the order of 1 to 2 bars, given by a electric pump of known type, so that, as soon as the hydraulic pressure disappears in the housing 53, the membrane 44 is pushed back to clear the passage 56.

    Il est également préférable qu'à l'endroit de chaque orifice de conduite 50 la membrane 44 soit munie d'une coupelle de renforcement 57, d'un diamètre supérieur à celui de l'orifice, ayant pour objet d'éviter que la membrane ne soit poussée par la pression dans l'orifice de la conduite 50 et ainsi détériorée.It is also preferable that at each conduit port 50 the membrane 44 is provided with a reinforcing cup 57, of a diameter greater than that of the orifice, the purpose of which is to prevent the membrane from being pushed by the pressure in the orifice of the pipe 50 and thus deteriorated.

    Il est aussi avantageux de conformer la membrane par moulage de façon qu'au repos, en l'absence de toute pression, elle remplisse le logement 53 et dégage le passage 56.It is also advantageous to mold the membrane in such a way that rest, in the absence of any pressure, it fills the housing 53 and releases the passage 56.

    Ainsi, la membrane 44 en se déformant entre une position où elle est au fond du logement 53 et une position où elle obture le conduit d'aspiration 50 joue le rôle d'un clapet anti-retour d'aspiration.Thus, the membrane 44 is deformed between a position where it is at the bottom of the housing 53 and a position where it closes the suction duct 50 plays the role a suction check valve.

    Il y a, bien évidemment, autant de conduits 50, logements 53, conduits 55, logements 54 qu'il y a d'alésages 12 et de chambres 13. There are, of course, as many conduits 50, housing 53, ducts 55, housing 54 there are bores 12 and rooms 13.

    La disposition ainsi décrite en relation avec la figure 9 est indépendante de la configuration de la pompe hydraulique I et peut être transposée dans la pompe des figures 6 à 7 comme cela est représenté figure 9.The arrangement thus described in relation with FIG. 9 is independent of the configuration of the hydraulic pump I and can be transposed into the pump of the Figures 6 to 7 as shown in Figure 9.

    Dans tous les exemples représentés aux figures I à 9, la pompe hydraulique I est une pompe à plateau oscillant ou plateau biais et les pistons sont des pistons axiaux.In all the examples represented in FIGS. 1 to 9, the hydraulic pump I is a swash plate pump or bias plate and the pistons are pistons Axial.

    Mais il est à remarquer que l'on peut obtenir le même résultat avec une pompe à pistons radiaux à la condition, essentielle, que les pistons soient creux et que leurs têtes reposent sur la came d'entraínement (jouant le même rôle que le plateau biais 1) par des plots de glissement venant chevaucher une lunule ; de façon qu'à la fin de chaque cycle de compression la chambre dans laquelle se déplace la membrane soit mise en communication directe avec la chambre d'admission du liquide hydraulique.But it should be noted that we can achieve the same result with a pump. radial pistons with the essential condition that the pistons are hollow and that their heads rest on the drive cam (playing the same role as the bias tray 1) by sliding studs overlapping a lunula; so that at the end of each compression cycle the chamber in which the membrane moves put in direct communication with the liquid intake chamber hydraulic.

    Une telle pompe à pistons radiaux est représentée à la figure 11.Such a radial piston pump is shown in FIG.

    Cette pompe comporte une came 101, qui est un excentrique porté par un arbre moteur 102, porté par des roulements 103. Chaque piston est un piston creux 104 contretenu par un ressort 107, de sorte que sa tête 104a soit en appui contre la came 101 par l'intermédiaire d'un plot de glissement 105 traversé par un orifice 106. La came 101 se débat dans une chambre 109 communiquant avec un réservoir de liquide hydraulique (non représenté). La communication entre la chambre 109 et l'intérieur de chaque piston creux 104 est établie lorsque le plot 105 chevauche la rainure 108 creusée dans la came 101.This pump comprises a cam 101, which is an eccentric carried by a tree motor 102, carried by bearings 103. Each piston is a hollow piston 104 counteracted by a spring 107, so that its head 104a bears against the cam 101 via a sliding stud 105 through which a hole 106. The cam 101 is struggling in a chamber 109 communicating with a reservoir hydraulic fluid (not shown). The communication between the room 109 and the inside of each hollow piston 104 is established when the stud 105 overlaps the groove 108 dug in the cam 101.

    La pompe Il est identique à celle de la figure 1, les mêmes éléments portant les mêmes références.The pump It is identical to that of Figure 1, the same elements bearing the same references.

    La came 101 correspond au plateau biais 1 ; les pistons 104 aux pistons 4 ; les plots 105 aux plots 5 ; la rainure 108 à la lunule 8 et la chambre 109 à la chambre 9.The cam 101 corresponds to the bias plate 1; the pistons 104 to the pistons 4; the pads 105 to the pads 5; the groove 108 to the lunula 8 and the chamber 109 to the chamber 9.

    Le fonctionnement de la pompe double (I-II) représenté à la figure 10 est identique à celui des pompes précédemment représentées.The operation of the double pump (I-II) shown in Figure 10 is identical to that of the pumps previously represented.

    Claims (27)

    1. Pump allowing any type of liquid to be pumped whilst transmitting to it a very high backflow pressure of the type formed by associating two pumps: a hydraulic pump (I) on one hand comprising a plurality of pistons (4, 104) and a skewed plate (1) or shaft (101): and a second pump (II) on the other hand whose mobile means which carry out the suction and backflow of the liquid to be pumped, are flexible membranes driven by an alternating movement in one direction then in another by moving the hydraulic liquid pumped and sucked by the first pump (I) characterised by the fact that the pistons (4, 104) of the first pump (I) are hollow and crossed by the hydraulic liquid which, during the suction phase, crosses a lunule (8, 108) hollowed into the face of the skewed plate (1) or shaft (101); the membrane which can be distorted (24, 44) being held up by a spring (15) such that at the end of the compression stroke of each piston (4, 104), communication is made between the chamber (12 - 13) where the hydraulic liquid flows back against the membrane (24, 44) and the suction chamber (9, 109), this liquid is then, on one hand, sucked by the movement of the piston (4, 104) and, on the other, flowed back by the membrane (24, 44) under the action of its spring (15) which ensures at the same time: an exchange between the hydraulic liquid heated by the compression and the non-heated liquid; and a return to the initial position of the membrane (24, 44).
    2. Pump according to claim 1 in which the first pump (I) or hydraulic pump is a pump with a skewed plate (1) and axial pistons (4) the said axial pistons being hollow and held up by springs (7, 7a) so that the head (4a) of each hollow piston (4) rests against the skewed plate (1) using a sliding stud (5) crossed by a central bore (6), this stud straddling a lunule (8) which is engraved on the face of the skewed plate (1) during the suction phase of the corresponding piston, in order, during this phase, to make direct communication between the chamber (9) with the skewed plate (1) and the chamber (13a) where the hydraulic liquid was back flowed during the compression phase.
    3. Pump according to claim 1 in which the first pump (1) or hydraulic pump is a pump with radial pistons (104) driven by a shaft (101); the said radial pistons (104) being hollow and held up by springs (107) so that the head (4a) of each hollow piston (104) rests against the shaft (101) using a sliding stud (105) crossed by a central bore (106), this stud straddling a lunule (108) which is engraved on the face of the shaft (101) during the suction phase of the corresponding piston, in order, during this phase, to make direct communication between the chamber (109) where the shaft (101) works and the chamber (13a) where the hydraulic liquid was back flowed during the compression phase.
    4. Pump according to claim 2 in which the second pump (II) comprises as many chambers or bores (13) as the first pump (I) contains bores (12), each chamber (13) of the second pump (II) communicating directly with the corresponding bore (12) of the first pump (I) so that each piston (4, 104) of the first pump (I) cyclically sucks and back flows the hydraulic liquid in the corresponding chamber (13) of the second pump (II).
    5. Pump according to claim 4 in which each bore (13) in the second pump (II) is divided into two parts (13a, 13b) by a membrane which can be distorted (24) and held up by a spring (15), the part (13a) which communicates with the corresponding bore (12) of the first pump (I) and taking the hydraulic liquid which has been back flowed and sucked by it; the other part (13b), fitted with suction valves (16) and backflow valves (17) sucking and back flowing the product to be pumped.
    6. Pump according to claim 5 in which each spring (15) is supported against the rear face of the corresponding flexible membrane (24) using a cap (20) shaped so as not to cause damage to the said rear face of the membrane (24).
    7. Pump according to one of the previous claims in which the chamber (9, 109) in which the heads (4a, 104) of pistons (4, 104) work is connected to a tank of hydraulic liquid.
    8. Pump according to claim 7 in which the tank (11) of hydraulic liquid is outside the first pump (I) and communicates with the latter by means of a pipe (10), which opens outs into the chamber (9).
    9. Pump according to claim 7 in which the tank (11) is formed from a cylindrical casing (23) surrounding the body (21) of the first pump and communicating with the chamber (9) using a plurality of orifices (22).
    10. Pump according to claim 2 in which the individual membranes (24), which can be distorted, are replaced by a single membrane (44) placed between the bores (12) of the pistons (4) and the chambers (13).
    11. Pump according to claim 10 in which a circular plate (42) is placed between the part (41) in which the bores (12) are housed and the part (45) in which the chambers (13) are fitted this part making each bore (12) communicate using drillings (43) with the corresponding chamber (13).
    12. Pump according to claim 10 in which each chamber (13) has a spring (15), which rests on the membrane (44) by means of a cap.
    13. Pump according to claim 12 in which each chamber (13) is linked to a one-way suction valve (16) and a one-way back flow valve (17).
    14. Pump according to claim 12 in which each chamber (13) is only linked to a one-way back flow valve (17), the one-way suction valve (16) being removed and its function carried out by the membrane (44) itself.
    15. Pump according to claim 14 in which the inlet pipe (5) for the liquid to be pumped opens out against the membrane (44) which is held against the opening of this pipe during the back flow phase and is moved aside during the suction phase.
    16. Pump according to claim 15 in which the part of the membrane (44) which rests against the opening (50) of the liquid inlet is fitted with a strengthening cap (57).
    17. Pump according to claim 15 in which during the suction phase the membrane (44) goes to the base of the housing (53) to free a communication passage (56) between the liquid inlet pipe (5) and the chamber (13).
    18. Pump according to claim 17 in which the membrane (44) is pre-shaped to occupy the base of the housing (53) during suction to free the passage (56).
    19. Pump according to any of the previous claims characterised by the fact that it is designed for high pressure supply to fuel injectors for internal combustion engines, the hydraulic liquid from the first pump (I) could be the oil for the said engine.
    20. Pump according to claim 19 characterised by the fact that it comprises means to make the flow of the hydraulic pump (I) vary, and, as a consequence, the flow of the pump (II) so as to adapt the flow of petrol which is pumped at a high pressure, towards the injectors when the engine is running.
    21. Pump according to claim 20 in which the skewed plate (1) of the hydraulic pump (I) is a plate whose incline can be varied.
    22. Pump according to claim 20 characterised by the fact that each piston (4) on the hydraulic pump (I) is fitted with openings (36) which can be hidden, fully or partially, using a mobile lining (34), all the mobile linings (34) being moved together by a command part (38) driven in running conditions of the engine.
    23. Device according to claim 22, in which the pistons slide in to supports (31, 32) drilled with orifices (33, 12), these two supports being separated from each other by an annular space making a chamber (35) in which the linings (34) move between two extreme positions: one where, since the orifices (36) are not hidden by the linings (34), all the liquid back flowed by each piston (4) flows into the annular chamber (35) through the piston orifices (36), the flow of pump (I) being nil; the other, where all the orifices (36) are hidden by the linings (34), each piston (4) back flows in volume all the sucked hydraulic liquid, the flow of pump (I) then being maximum.
    24. Device according to claim 23 in which the linings (34) can occupy all the intermediary positions between the two extreme positions: so that the flow of pump (I) can be regulated for all values between zero flow and maximum flow.
    25. Device according to claim 24 in which all the linings (34) are coupled to a common command part (38) which is driven by any appropriate command device to regulate the high pressure flow of petrol according to the supply requirements of the engine without the high pressure petrol returning to the tank.
    26. Device according to claim 25, in which a shock absorber device is placed upstream of the outlet (29) of the second pump (II) and downstream of the injectors to cancel the pulsating effect brought about by the first pump (I).
    27. Device according to claim 26, in which the shock absorber device is significant volume capacity in relation to the flow of petrol, kept under injection pressure by any appropriate means in the manner of a hydraulic accumulator.
    EP00202790A 1996-06-07 1997-05-30 High pressure liquid pump Expired - Lifetime EP1048849B1 (en)

    Applications Claiming Priority (5)

    Application Number Priority Date Filing Date Title
    FR9607043A FR2749616B1 (en) 1996-06-07 1996-06-07 HIGH PRESSURE PUMP FOR ALL LIQUIDS
    FR9607043 1996-06-07
    FR9613502 1996-11-06
    FR9613502A FR2755472B1 (en) 1996-11-06 1996-11-06 HIGH PRESSURE FEEDING DEVICE FOR FUEL INJECTORS FOR INTERNAL COMBUSTION ENGINES
    EP97926060A EP0901575B1 (en) 1996-06-07 1997-05-30 High pressure pump for all liquids

    Related Parent Applications (1)

    Application Number Title Priority Date Filing Date
    EP97926060A Division EP0901575B1 (en) 1996-06-07 1997-05-30 High pressure pump for all liquids

    Publications (2)

    Publication Number Publication Date
    EP1048849A1 EP1048849A1 (en) 2000-11-02
    EP1048849B1 true EP1048849B1 (en) 2005-03-16

    Family

    ID=26232746

    Family Applications (2)

    Application Number Title Priority Date Filing Date
    EP97926060A Expired - Lifetime EP0901575B1 (en) 1996-06-07 1997-05-30 High pressure pump for all liquids
    EP00202790A Expired - Lifetime EP1048849B1 (en) 1996-06-07 1997-05-30 High pressure liquid pump

    Family Applications Before (1)

    Application Number Title Priority Date Filing Date
    EP97926060A Expired - Lifetime EP0901575B1 (en) 1996-06-07 1997-05-30 High pressure pump for all liquids

    Country Status (7)

    Country Link
    US (1) US6264437B1 (en)
    EP (2) EP0901575B1 (en)
    JP (1) JP3990732B2 (en)
    DE (1) DE69732802T2 (en)
    ES (1) ES2238968T3 (en)
    PT (1) PT1048849E (en)
    WO (1) WO1997047883A1 (en)

    Families Citing this family (26)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    US6035828A (en) 1998-03-11 2000-03-14 Caterpillar Inc. Hydraulically-actuated system having a variable delivery fixed displacement pump
    DE59809021D1 (en) * 1998-05-20 2003-08-21 Wagner Ag Altstaetten J DIAPHRAGM PUMP FOR CONVEYING HIGH-VISCUS MEDIA
    FR2794810B1 (en) 1999-06-08 2001-08-31 Peugeot Citroen Automobiles Sa IMPROVED HIGH PRESSURE PUMP
    FR2794811B1 (en) * 1999-06-08 2003-02-07 Peugeot Citroen Automobiles Sa HIGH PRESSURE PUMP WITH IMPROVED SEALING
    FR2794813B1 (en) 1999-06-08 2001-09-21 Peugeot Citroen Automobiles Sa HIGH PRESSURE PUMP WITH IMPROVED FILLING CAP
    FR2794812B1 (en) 1999-06-08 2003-02-21 Peugeot Citroen Automobiles Sa HIGH PRESSURE PUMP WITH IMPROVED HUB
    US6561771B2 (en) 2001-06-19 2003-05-13 Caterpillar Inc Axial piston pump with center inlet fill
    JP3719990B2 (en) * 2002-02-15 2005-11-24 株式会社デンソー Compressor
    US7125230B2 (en) 2002-07-09 2006-10-24 Caterpillar Inc Valve with operation parameter set at assembly and pump using same
    US6901911B2 (en) 2002-07-31 2005-06-07 Caterpillar Inc Pump and hydraulic system with low pressure priming and over pressurization avoidance features
    WO2004031569A1 (en) * 2002-10-02 2004-04-15 Bosch Automotive Systems Corpopation Diesel engine fuel feeder
    US6802697B2 (en) 2002-12-30 2004-10-12 Caterpillar Inc Variable-delivery, fixed-displacement pump
    DE102004004705A1 (en) * 2004-01-30 2005-08-18 Robert Bosch Gmbh High-pressure pump, in particular for a fuel injection device of an internal combustion engine
    US20060168955A1 (en) * 2005-02-03 2006-08-03 Schlumberger Technology Corporation Apparatus for hydraulically energizing down hole mechanical systems
    FR2883932B1 (en) * 2005-04-04 2007-06-22 Siemens Automotive Hydraulics IMPROVEMENT IN TRANSFER PUMPS
    US7428812B2 (en) * 2006-05-04 2008-09-30 Fci Americas Technology, Inc. Hydraulic tool with wobble plate transmission
    US7487654B2 (en) * 2006-10-13 2009-02-10 Fci Americas Technology, Inc. Hydraulic tool with tactile feedback
    US8122585B2 (en) * 2007-02-20 2012-02-28 Hubbell Incorporated Spanner plate
    CN102979696B (en) * 2012-12-03 2015-05-13 常州富邦电气有限公司 Double inlet efficiency air pump
    US9909576B2 (en) 2015-01-23 2018-03-06 Caterpillar Inc. Pump drive system with hydraulic tappets
    US20170030341A1 (en) * 2015-07-27 2017-02-02 Caterpillar Inc. Multi-plunger cryogenic pump having intake manifold
    US10024311B2 (en) * 2015-08-06 2018-07-17 Caterpillar Inc. Cryogenic pump for liquefied natural gas
    US9915250B2 (en) * 2015-08-24 2018-03-13 Caterpillar Inc. Hydraulic drive system for cryogenic pump
    US10190556B2 (en) * 2017-01-09 2019-01-29 Caterpillar Inc. System and method for lubricating a cryogenic pump
    DE102018200715A1 (en) * 2018-01-17 2019-07-18 Robert Bosch Gmbh Fuel delivery device for cryogenic fuels
    DE102018211338A1 (en) * 2018-07-10 2020-01-16 Robert Bosch Gmbh Fuel delivery device for cryogenic fuels and method for operating a fuel delivery device

    Family Cites Families (27)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    US2301407A (en) * 1940-06-22 1942-11-10 Dayton Liquid Meter Company Fuel injection pump
    US2433222A (en) * 1945-11-05 1947-12-23 New York Air Brake Co Pump
    FR1122769A (en) * 1954-04-17 1956-09-12 Injection pump for combustion engines
    US2960936A (en) * 1958-07-11 1960-11-22 William M Dean Fuel injection pump
    FR1211846A (en) * 1958-10-18 1960-03-18 Hydraulic pump for agricultural sprayers
    US3680981A (en) * 1970-12-21 1972-08-01 Josef Wagner Pump and method of driving same
    SE358711B (en) * 1971-12-06 1973-08-06 Atlas Copco Ab
    FR2162332B2 (en) 1971-12-10 1976-10-29
    JPS4963003A (en) * 1972-06-16 1974-06-19
    US3884598A (en) * 1973-10-05 1975-05-20 Wanner Engineering Piston assembly for diaphragm pump
    GB1457487A (en) * 1974-06-19 1976-12-01 Leduc G Hydraulic swash plate pumps
    DE2946529A1 (en) * 1979-11-17 1981-05-27 Frieseke & Hoepfner Gmbh, 8520 Erlangen PRESSURE-CONTROLLED MULTI-CYLINDER PISTON PUMP
    US4443160A (en) * 1980-11-13 1984-04-17 Brueninghaus Hydraulik Gmbh High-pressure piston pump for liquids, preferably for water
    US4392787A (en) * 1981-01-21 1983-07-12 Wetrok Inc. Diaphragm pump
    EP0085725B1 (en) * 1982-02-05 1984-11-28 Bran & Lübbe GmbH Piston-driven diaphragm pump
    DE3414006C2 (en) * 1984-04-13 1986-03-06 Bran & Lübbe GmbH, 2000 Norderstedt Piston diaphragm pump
    US4667638A (en) * 1984-04-17 1987-05-26 Nippon Soken, Inc. Fuel injection apparatus for internal combustion engine
    CA1233363A (en) * 1984-06-01 1988-03-01 Robert E. Fischell Single valve diaphragm pump with decreased sensitivity to ambient conditions
    DE3446914A1 (en) * 1984-12-21 1986-07-03 Ott Kg Lewa DIAPHRAGM PUMP WITH HYDRAULICALLY DRIVED ROLLER
    ES2022824B3 (en) * 1987-02-28 1991-12-16 Bran & Luebbe MEMBRANE PUMP PUMP
    JPH0223829Y2 (en) * 1987-05-19 1990-06-28
    US4964345A (en) * 1987-12-18 1990-10-23 Hydro Rene Leduc Rail car axle with axial hydraulic pump
    DE3838141C2 (en) * 1988-11-10 1998-12-24 Knf Neuberger Gmbh Diaphragm pump
    DE4141670C2 (en) * 1991-12-17 1994-09-29 Ott Kg Lewa Hydraulically driven diaphragm pump with diaphragm stroke limitation
    DE4327970C2 (en) * 1993-08-19 1997-07-03 Ott Kg Lewa Hydraulically driven diaphragm pump with mechanical diaphragm stroke limitation
    FR2721352B1 (en) * 1994-06-17 1996-09-06 Leduc Rene Hydro Sa High pressure pump to supply fuel injectors for internal combustion engines.
    US5707219A (en) * 1995-10-04 1998-01-13 Wanner Engineering Diaphragm pump

    Also Published As

    Publication number Publication date
    EP0901575A1 (en) 1999-03-17
    JP2000511989A (en) 2000-09-12
    EP0901575B1 (en) 2011-06-01
    DE69732802T2 (en) 2006-04-06
    PT1048849E (en) 2005-05-31
    WO1997047883A1 (en) 1997-12-18
    DE69732802D1 (en) 2005-04-21
    JP3990732B2 (en) 2007-10-17
    EP1048849A1 (en) 2000-11-02
    US6264437B1 (en) 2001-07-24
    ES2238968T3 (en) 2005-09-16

    Similar Documents

    Publication Publication Date Title
    EP1048849B1 (en) High pressure liquid pump
    FR2758372A1 (en) COMPRESSOR FOR VEHICLE INTERIOR AIR CONDITIONING SYSTEM
    EP0558389B1 (en) Hydraulic piston pump with inlet valves
    EP0082039B1 (en) Hydrostatic clutch
    FR2680392A1 (en) PRIMER PUMP STAGE PUMP ARRANGEMENT AND UPSTREAM GAS PUMP.
    EP3145745A1 (en) Vehicle-mounted hydraulic assistance device and method for evacuating such a device
    FR2825419A1 (en) PUMP IN PARTICULAR FOR LUBRICATING OIL OF INTERNAL COMBUSTION ENGINES WHOSE TRANSPORTED VOLUME IS ADJUSTABLE ACCORDING TO TEMPERATURE
    FR2525697A1 (en) TWO STAGE VOLUMETRIC PUMP FOR LIQUEFIED LIQUID PHASE OIL GASES, AND FUEL INJECTION METHOD FOR MOTOR VEHICLE ENGINE USING SUCH PUMP
    FR2862354A1 (en) Variable displacement pump e.g. vane pump, for internal combustion engine, has nesting ring moved transversally with respect to rotor in chamber which has sealing units acting on rings flat wheels supported on surface of chamber
    WO2018229368A1 (en) Expansion machine and methods for using such a machine
    EP1999372A1 (en) Transfer pump for high-pressure petrol injection
    EP0731886B1 (en) Device for lubricating a coupling between two mutually movable mechanical parts, particularly a connecting rod/piston coupling
    FR2711736A1 (en) Liquid fuel injection device for diesel engine.
    FR2749616A1 (en) High pressure pump for liquids e.g. water, petrol, oil, or chemicals
    FR2978207A1 (en) COOLING AGENT PUMP FOR A COOLING CIRCUIT OF AN INTERNAL COMBUSTION ENGINE
    EP0283348A1 (en) Hydraulic pumps
    EP0466561A1 (en) Hydraulic machine with rotating cylinder block
    FR2746455A1 (en) VALVE STRUCTURE IN A COMPRESSOR
    EP0180510B1 (en) Hydraulic piston pump with positively driven inlet valves
    FR2822199A1 (en) Hydraulic piston pump comprises body, drive shaft and eccentric, radial pistons coupled to eccentric translate in chambers inside body and distributor with fluid inlet and outlet manages fluid flow in chambers
    FR2881478A1 (en) PILOT INJECTION PUMP
    FR2755472A1 (en) High=pressure pump for all liquids, for i.c. engine fuel injection
    EP0061405B1 (en) Hydraulic pistion pump with a variable stroke, and pressure-fluid generator using such a pump
    FR2826068A1 (en) Flow regulation device for fuel transfer pump comprises chambers, receiving high pressure oil, though non-return valve to common manifold connected to electrical valve regulating flow
    FR2518657A1 (en) CLOSING PISTON FOR FIXED CYLINDER PUMP

    Legal Events

    Date Code Title Description
    PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

    Free format text: ORIGINAL CODE: 0009012

    AC Divisional application: reference to earlier application

    Ref document number: 901575

    Country of ref document: EP

    AK Designated contracting states

    Kind code of ref document: A1

    Designated state(s): DE ES FR GB IT PT SE

    17P Request for examination filed

    Effective date: 20000930

    AKX Designation fees paid

    Free format text: DE ES FR GB IT PT SE

    GRAP Despatch of communication of intention to grant a patent

    Free format text: ORIGINAL CODE: EPIDOSNIGR1

    GRAS Grant fee paid

    Free format text: ORIGINAL CODE: EPIDOSNIGR3

    GRAA (expected) grant

    Free format text: ORIGINAL CODE: 0009210

    RAP1 Party data changed (applicant data changed or rights of an application transferred)

    Owner name: HYDRO LEDUC

    AC Divisional application: reference to earlier application

    Ref document number: 0901575

    Country of ref document: EP

    Kind code of ref document: P

    AK Designated contracting states

    Kind code of ref document: B1

    Designated state(s): DE ES FR GB IT PT SE

    REG Reference to a national code

    Ref country code: GB

    Ref legal event code: FG4D

    Free format text: NOT ENGLISH

    REF Corresponds to:

    Ref document number: 69732802

    Country of ref document: DE

    Date of ref document: 20050421

    Kind code of ref document: P

    GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

    Effective date: 20050420

    REG Reference to a national code

    Ref country code: PT

    Ref legal event code: SC4A

    Free format text: AVAILABILITY OF NATIONAL TRANSLATION

    Effective date: 20050329

    REG Reference to a national code

    Ref country code: SE

    Ref legal event code: TRGR

    REG Reference to a national code

    Ref country code: ES

    Ref legal event code: FG2A

    Ref document number: 2238968

    Country of ref document: ES

    Kind code of ref document: T3

    PLBE No opposition filed within time limit

    Free format text: ORIGINAL CODE: 0009261

    STAA Information on the status of an ep patent application or granted ep patent

    Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

    26N No opposition filed

    Effective date: 20051219

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: PT

    Payment date: 20060426

    Year of fee payment: 10

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: SE

    Payment date: 20060518

    Year of fee payment: 10

    REG Reference to a national code

    Ref country code: PT

    Ref legal event code: MM4A

    Free format text: LAPSE DUE TO NON-PAYMENT OF FEES

    Effective date: 20071130

    EUG Se: european patent has lapsed
    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: PT

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20071130

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: SE

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20070531

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: DE

    Payment date: 20120514

    Year of fee payment: 16

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: GB

    Payment date: 20120521

    Year of fee payment: 16

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: IT

    Payment date: 20120522

    Year of fee payment: 16

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: ES

    Payment date: 20120524

    Year of fee payment: 16

    GBPC Gb: european patent ceased through non-payment of renewal fee

    Effective date: 20130530

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: DE

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20131203

    REG Reference to a national code

    Ref country code: DE

    Ref legal event code: R119

    Ref document number: 69732802

    Country of ref document: DE

    Effective date: 20131203

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: IT

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20130530

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: GB

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20130530

    REG Reference to a national code

    Ref country code: ES

    Ref legal event code: FD2A

    Effective date: 20140606

    PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

    Ref country code: ES

    Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

    Effective date: 20130531

    REG Reference to a national code

    Ref country code: FR

    Ref legal event code: PLFP

    Year of fee payment: 20

    PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

    Ref country code: FR

    Payment date: 20160527

    Year of fee payment: 20