EP0901575B1 - Hochdruckpumpe für alle flüssigkeiten - Google Patents

Hochdruckpumpe für alle flüssigkeiten Download PDF

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Publication number
EP0901575B1
EP0901575B1 EP97926060A EP97926060A EP0901575B1 EP 0901575 B1 EP0901575 B1 EP 0901575B1 EP 97926060 A EP97926060 A EP 97926060A EP 97926060 A EP97926060 A EP 97926060A EP 0901575 B1 EP0901575 B1 EP 0901575B1
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EP
European Patent Office
Prior art keywords
pump
chamber
diaphragm
liquid
pump according
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
EP97926060A
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English (en)
French (fr)
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EP0901575A1 (de
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/fr
Priority claimed from FR9613502A external-priority patent/FR2755472B1/fr
Application filed by Hydro Leduc SAS filed Critical Hydro Leduc SAS
Priority to EP00202790A priority Critical patent/EP1048849B1/de
Publication of EP0901575A1 publication Critical patent/EP0901575A1/de
Application granted granted Critical
Publication of EP0901575B1 publication Critical patent/EP0901575B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 present invention relates to a pump capable of pumping and discharging under high pressure virtually any liquid such as: water, gasoline, diesel, oils, corrosive chemical liquids and sludge; but more particularly for the high pressure supply of fuel injectors for internal combustion engines.
  • the membrane is on one side driven by mechanical means (cam, lever or the like) and is on the other subject to the discharge pressure: it follows that as soon as the pressure becomes high the membrane deteriorates at the points of application of the mechanical forces.
  • a first pump which is a hydraulic pump which represses and re-aspirates hydraulic fluid which moves the moving parts of 'a second pump, the latter sucking and pressurizing the liquid to be pumped.
  • movable elements which ensure the physical separation between the hydraulic fluid and the liquid to be pumped, while being reciprocated by the hydraulic fluid, are either deformable membranes or free pistons.
  • the free pistons have a fault with regard to the sealing, a defect that is unavoidable in cases where one must have an absolute seal. If a seal is placed 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 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 leakage, no matter how small, is permissible and, of course, any heating may cause an explosion.
  • the present invention therefore relates to a pumping device in which the moving elements, driven by an alternating pumping movement by the hydraulic pump and ensuring a completely sealed separation between the hydraulic fluid "motor” and the liquid to be pumped are deformable membranes.
  • the present invention proposes a device in 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 (compression position maximum), in which the liquid in contact with the membrane is placed in communication with the reserve of hydraulic fluid; so that the liquid in it is pushed back to this reserve first by the expansion of the liquid, then by the effect of discharge by the membrane which is realizedtentioned by a spring.
  • the present invention relates to a pump according to claim 1.
  • 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 reciprocated back and forth by a bias plate 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 bear 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 its stud.
  • On the front face 1 is engraved a lunula 8.
  • This chamber 9 opens, by a plurality of holes 22, passing through the body 21 of the pump I, in a reservoir 11.
  • This reservoir 11 is constituted by a cylindrical envelope 23 which surrounds the body 21.
  • the side of the bias plate 1 oscillates in the chamber 9 so that the pistons 4 are reciprocated in a reciprocating movement: in the direction corresponding to the suction, the pistons 4 are driven by their spring 7; in the other direction which corresponds to the pressure discharge, they are pushed against the spring 7 by the bias plate 1.
  • the hydraulic fluid in the chamber 9 enters the interior of 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 it can exceed 1000 bar with this type of pump).
  • none of the bores 12 in which the pistons 4 slide have a non-return valve.
  • a pump II is associated with the pump I immediately downstream thereof.
  • each bore 12 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 portion 13a communicates directly with the end of the bore 12, while the portion 13b is provided at its end opposite the membrane 24 of a suction valve 16 and a discharge valve 17. All the valves 17 flow into 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 rear face 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 of sucking the product to be pumped into the portion 13b of the bore 13, through the non-return valve 16 and to discharge the hydraulic fluid found in Part 13a.
  • the product to be pumped is alternately sucked and then discharged by the reciprocating movement of the membranes 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 volume variations being caused by the alternations of delivery and suction of the hydraulic fluid by the pistons 4 of the first pump I.
  • Each membrane 24 is subjected, on its two front and rear faces and this uniformly distributed over the entire surface of the membrane, at the same pressure: on one side the pressure of the hydraulic fluid motor, on the other the pressure of the repressed liquid.
  • the membrane therefore undergoes no mechanical stress and can not tear.
  • the pump according to the present invention is therefore a diaphragm pump in which each diaphragm is, in the discharge phase, in equipressure on each side, which makes it possible to have a discharge pressure equal to hydraulic pressure that can provide the first pump I.
  • the pump according to the present invention can be used, inter alia, to pressurize liquids having no grinding power.
  • it can be used to supply internal combustion engine injectors (motor car engines) fed with super-fuel and / or liquid LPG as a substitute fuel, for example.
  • the super-fuel is sucked by the valves 16, discharged under high pressure (more than 50 bar) by the valves 17 without the fuel is never brought into contact with metal members to slide against each other.
  • the motor oil itself can advantageously be used as hydraulic fluid by directly communicating the chamber 9 with the engine oil distribution circuit, the temperature of this oil being regulated by the appropriate engine components.
  • the pump according to the invention can also be used to circulate under pressure the drilling muds.
  • the suction force of the second pump II which is related 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 for supplying an engine
  • the first solution consists in producing the first pump I in the form of a variable flow pump by using a variable inclination bias plate 1 as is done in certain pumps produced by the applicant.
  • 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 for canceling in whole or in part the flow pumped by said piston.
  • each hollow piston 4 is traversed right through by a pipe 30.
  • the pistons 4 are carried by two supports 31 and 32 pierced with orifices 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 the support 32 is greater 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 sliding jacket 34.
  • These sliding folders are all connected to a connecting rod. 38 so as to slide all together between two extreme positions, the first being illustrated in FIG. figure 3 the second being illustrated in figure 4 .
  • said jackets 34 conceal the holes 36 which communicate the internal pipe 30 of each piston 4 with the annular chamber 35.
  • the shirts 34 discover said holes 36.
  • the pusher 7b, counteracting the flange 6 of each piston head is traversed by a pipe 37 which communicates with each other the two chambers 9 and 35.
  • the output flow rate of the pump II is regulated according to the flow rate of gasoline that is required for the injection and that excess fuel returns to the reservoir are minimized to the maximum.
  • the gas flow thus obtained is a pulsed flow.
  • the shirts 34 are in a position such that only 10% of the maximum flow rate of the pump I is delivered in the portion 13a of the volume 13, this means that this pump 1 provides no flow for 90% of the stroke of each piston or that there is flow on only 10% of the stroke of each piston. This has the effect that the flow is a pulsed flow.
  • This device may advantageously be constituted in a similar manner to a hydraulic accumulator that is to say constituted by a capacity having a large volume compared to the flow rate supplied to the injectors and kept under constant pressure.
  • the figure 6 represents a pump similar to the pump of the figure 1 in which the same elements bear the same references.
  • the tank 11 of the figure 1 which envelops the hydraulic pump is replaced by an outer tank 11a; for the rest, all the components are identical with the sole exception of the membrane of the pump II of the figure 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.
  • the pump of the figure 6 like that of the figure 1 , comprises a one-piece pump housing 40, in two cylindrical portions 40a and 40b, the portion 40b having an internal diameter greater than that of the portion 40a.
  • the bearings 3 In the part 40a are arranged the bearings 3, the drive shaft 2, the bias plate 1, the feed chamber 9 and the rear portion 41a of a part 41 in which the bores 12 are drilled.
  • the front part 41b of this piece is in the portion 40b of greater diameter of the housing 40; so that this front portion 41b rests against the shoulder separating the two parts 40a and 40b of the casing 40.
  • the bores 12 of the pistons 4 open to the front face of this portion 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 holes 43 as there are bores 12 and chamber 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 shape of a disk having the same diameter as the plate 42. The membrane 44 is clamped between the plate 42 and the end of the part 45.
  • Each bore 43 communicates with a bore 12 of the pump I and is opposite a volume 13.
  • the figure 9 represents an alternative embodiment of the pump of Figures 6 to 8 .
  • the essential difference relates to the mechanical constitution of the hydraulic pump I.
  • This hydraulic pump I has, like the pumps of the figures 1 , 3 and 6 , a bias plate 1 against which hollow pistons 4 rest by means of sliding studs 5, pierced with a bore 6 intended to overlap a lunula 8. But in the previously described pumps, the bias plate 1 is disposed at the end of a motor shaft 2 carried by bearings 3; while in the pump the figure 9 , the bias plate 1 is integrated in a ball bearing.
  • This ball bearing comprises an outer cage 61 fixed inside the casing 60 of the pump and an inner cage 62 to which is fixed the bias plate 1, a set of balls 63 being disposed between the two cages 61 and 62.
  • the bias plate 1 comprises a housing 64 in which can be inserted into the end of a motor shaft not shown.
  • each duct 13 is associated with a duct 50 connected to a chamber 51 where the liquid to be pumped arrives via a duct 52.
  • the duct 50 is pierced through the mass of the room 45 and opens at its opposite end to 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 part 45, in which are formed the chambers 13 comprises two housings 53 and 54 connected by a pipe 55.
  • the housing 53 is hollowed in the face of the part 42 which is in contact with the membrane 44; while the housing 54 is hollowed in the face which is in contact with the part 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 liquid to be pumped (which is, for example, gasoline) arrives through the pipe 52 at a low pressure, of the order of 1 to 2 bars, given by an 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.
  • 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 is pushed by the pressure in the orifice of the pipe 50 and thus deteriorated.
  • the membrane 44 by deforming between a position where it is at the bottom of the housing 53 and a position where it closes the suction duct 50 acts as a suction check valve.
  • the hydraulic pump I is a swash plate pump or bias plate and the pistons are axial pistons.
  • FIG. figure 11 Such a radial piston pump which is not part of the invention is shown in FIG. figure 11 .
  • This pump comprises a cam 101, which is an eccentric carried by a motor shaft 102, carried by bearings 103.
  • Each piston is a hollow piston 104 cortenu by a spring 107, so that its head 104a bears against the cam 101 by means of a sliding stud 105 traversed by an orifice 106.
  • the cam 101 is struggling in a chamber 109 communicating with a reservoir of hydraulic fluid (not shown). The communication between the chamber 109 and the interior of each hollow piston 104 is established when the stud 105 overlaps the groove 108 made in the cam 101.
  • 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.

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

Claims (17)

  1. Pumpe, die ein Pumpen von Flüssigkeit jeglicher Art zuläßt, indem sie dieser einen sehr hohen Förderdruck aufprägt, der Art, die durch einen Verbund zweier Pumpen gebildet ist:
    einerseits aus einer hydraulischen Pumpe (I), die eine Vielzahl von Kolben (4, 104) und eine Taumelscheibe (1) umfaßt, andererseits aus einer zweiten Pumpe (II), deren bewegliche Mittel, welche das Ansaugen und das Fördern der zu pumpenden Flüssigkeit bewirken, nachgiebige Membrane sind, die zu einer wechselnden Bewegung in eine und dann die andere Richtung durch das Verdrängen der von der ersten Pumpe (I) gepumpten und dann wieder angesaugten hydraulischen Flüssigkeit angeregt werden, wobei die Kolben (4, 104) der ersten Pumpe (I) hohl sind und von der hydraulischen Flüssigkeit durchströmt werden, die während der Ansaugphase durch eine sichelförmige Ausnehmung (8, 108) hindurchtritt, die in die Vorderfläche der Taumelscheibe (1) eingebracht ist, wobei ferner die verformbare Membran (24, 44) von einer Feder (15) vorgespannt ist derart, daß am Ende des Kompressionshubes jedes Kolbens (4, 104) die Verbindung zwischen der Kammer (12, 13), wo sich die gegen die Membran (24, 44) geförderte hydraulische Flüssigkeit befindet, und der Ansaugkammer (9, 109) hergestellt ist, wobei dann diese Flüssigkeit einerseits von der Bewegung des Kolbens (4, 104) angesaugt und andererseits durch die Membran (24, 44) unter Einwirkung deren Feder (15) gefördert wird, was gleichzeitig einen Austausch zwischen der durch die Kompression erwärmten und der nicht erwärmten Flüssigkeit und ein Zurückkehren der Membran (24, 44) in ihre Ausgangsstellung gewährleistet, und wobei die erste Pumpe (I) oder hydraulische Pumpe eine Pumpe mit Taumelscheibe (1) und mit Axialkolben (4) ist, wobei die Axialkolben hohl und von Federn (7, 7a) vorgespannt sind derart, daß der Kopf (4a) jedes Hohlkolbens (4) gegen die Taumelscheibe (1) unter Zwischenschaltung eines Gleitsteines (5) anliegt, der von einer zentralen Bohrung (6) durchsetzt ist, wobei der Stein während der Ansaugphase des zugehörigen Kolbens eine sichelförmige Ausnehmung (8), die auf der Vorderseite der Taumelscheibe (1) eingebracht ist, überdeckt, so daß während dieser Phase eine direkte Verbindung zwischen der Kammer (9), in welcher sich die Taumelscheibe bewegt, und der Kammer (13a) hergestellt ist, in welche die hydraulische Flüssigkeit während der Kompressionsphase gefördert wurde, und wobei die Taumelscheibe (1) in dem Innenring (62) eines Kugellagers (63) befestigt ist, dessen Außenring (61) direkt in einem Gehäuse (60) der Pumpe befestigt ist.
  2. Pumpe nach Anspruch 1, bei der die zweite Pumpe (II) ebenso viele Kammern oder Öffnungen (13) wie die erste Pumpe (I) Bohrungen (12) umfaßt, wobei jede Kammer (13) der zweiten Pumpe (II) direkt mit der zugeordneten Bohrung (12) der ersten Pumpe (I) in Verbindung steht derart, daß jeder Kolben (4, 104) der ersten Pumpe (I) zyklisch die hydraulische Flüssigkeit in der entsprechenden Kammer (13) der zweiten Pumpe (II) fördert und ansaugt.
  3. Pumpe nach Anspruch 2, bei der jede Öffnung (13) der zweiten Pumpe (II) in zwei Abschnitte (13a, 13b) durch eine verformbare Membran (24) aufgeteilt ist, die von einer Feder (15) vorgespannt ist, wobei der Abschnitt (13a) mit der entsprechenden Bohrung (12) der ersten Pumpe (I) in Verbindung steht und die von dieser geförderte und angesaugte hydraulische Flüssigkeit aufnimmt, während er andere Abschnitt (13b), der mit Ventilen zum Ansaugen (16) und Fördern (17) versehen ist, das zu pumpende Produkt ansaugt und fördert.
  4. Pumpe nach Anspruch 3, bei der jede Feder (15) gegen die Rückseite der entsprechenden biegsamen Membran (24) unter Zwischenschaltung einer Kappe (20) anliegt, die so gestaltet ist, daß sie keine Zerstörung dieser Rückseite der Membran (24) bewirkt.
  5. Pumpe nach einem der vorangehenden Ansprüche, bei der die Kammer (9, 109), in der sich die Köpfe (4a, 104a) der Kolben (4, 104) verschwenken, an einen Speicher von hydraulischer Flüssigkeit angeschlossen ist.
  6. Pumpe nach Anspruch 5, bei welcher der Speicher (11) mit hydraulischer Flüssigkeit außerhalb der ersten Pumpe (I) angebracht ist und mit dieser letzteren durch eine Leitung (10), die in die Kammer (9) mündet, in Verbindung steht.
  7. Pumpe nach Anspruch 5, bei welcher der Speicher (11) von einer zylindrischen Einhausung (23) gebildet wird, die den Körper (21) der ersten Pumpe umgibt und mit der Kammer (9) über eine Vielzahl von Öffnungen (22) in Verbindung steht.
  8. Pumpe nach Anspruch 1, bei der die einzelnen verformbaren Membrane (24) durch eine einzige Membran (44) ersetzt sind, die zwischen die Bohrungen (12) der Kolben (4) und den Kammern (13) zwischengeschaltet sind.
  9. Pumpe nach Anspruch 8, bei der eine Kreisplatte (42) zwischen dem Teil (41), in das die Bohrungen (12) eingebracht sind, und dem Teil (45), in dem die Kammern (13) ausgebildet sind, zwischengeschaltet ist, wobei dieses Stück über Öffnungen (43) jede Bohrung (12) mit der ihr entsprechenden Kammer (13) in Verbindung bringt.
  10. Pumpe nach Anspruch 8, bei der in jeder Kammer (13) eine Feder (15) vorgesehen ist, die mittels einer Kappe (20) auf der Membran (44) zur Anlage kommt.
  11. Pumpe nach Anspruch 9, bei der jede Kammer (13) an ein Ansaug-Rückschlagventil (16) und an ein Förder-Rückschlagventil (17) angeschlossen ist.
  12. Pumpe nach Anspruch 10, bei der jede Kammer (13) nur an ein Förder-Rückschlagventil (17) angeschlossen ist, wobei das Ansaug-Rückschlagventil (16) weggelassen ist und seine Funktion von der Membran (44) selbst erfüllt wird.
  13. Pumpe nach Anspruch 12, bei der die Speiseleitung (50) der zu pumpenden Flüssigkeit gegen die Membran (44) mündet, die in Anlage gegen die Öffnung dieser Leitung während der Förderphase gehalten wird und während der Ansaugphase von dieser getrennt ist.
  14. Pumpe nach Anspruch 13, bei welcher der Abschnitt der Membran (44), der gegen die Einlaßöffnung (50) der Flüssigkeit zur Anlage kommt, mit einer Verstärkungskappe (57) versehen ist.
  15. Pumpe nach Anspruch 13, bei der während der Ansaugphase die Membran (44) auf den Boden einer Ausnehmung (53) gelangt, um einen Verbindungskanal (56) zwischen der Speiseleitung (50) der Flüssigkeit und der Kammer (13) frei zu machen.
  16. Pumpe nach Anspruch 15, bei der die Membran (44) durch Guß vorgeformt ist, um den Boden der Ausnehmung (53) während des Ansaugens zum Freigeben des Kanals (56) zu bedecken.
  17. Pumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß sie zur Hochdruck-Beaufschlagung von Benzin-Einspritzdüsen für Brennkraftmotoren bestimmt ist, wobei die hydraulische Flüssigkeit der ersten Pumpe (1) das Öl dieses Motors sein kann.
EP97926060A 1996-06-07 1997-05-30 Hochdruckpumpe für alle flüssigkeiten Expired - Lifetime EP0901575B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00202790A EP1048849B1 (de) 1996-06-07 1997-05-30 Flüssigkeitshochdruckpumpe

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
FR9607043 1996-06-07
FR9607043A FR2749616B1 (fr) 1996-06-07 1996-06-07 Pompe a haute pression pour tous liquides
FR9613502A FR2755472B1 (fr) 1996-11-06 1996-11-06 Dispositif d'alimentation a haute pression d'injecteurs d'essence pour moteurs a combustion interne
FR9613502 1996-11-06
PCT/FR1997/000943 WO1997047883A1 (fr) 1996-06-07 1997-05-30 Pompe a haute pression pour tous liquides

Related Child Applications (3)

Application Number Title Priority Date Filing Date
EP00202790A Division EP1048849B1 (de) 1996-06-07 1997-05-30 Flüssigkeitshochdruckpumpe
EP00202790.2 Division-Into 2000-08-07
EP05025334.3 Division-Into 2005-11-21

Publications (2)

Publication Number Publication Date
EP0901575A1 EP0901575A1 (de) 1999-03-17
EP0901575B1 true EP0901575B1 (de) 2011-06-01

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP97926060A Expired - Lifetime EP0901575B1 (de) 1996-06-07 1997-05-30 Hochdruckpumpe für alle flüssigkeiten
EP00202790A Expired - Lifetime EP1048849B1 (de) 1996-06-07 1997-05-30 Flüssigkeitshochdruckpumpe

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP00202790A Expired - Lifetime EP1048849B1 (de) 1996-06-07 1997-05-30 Flüssigkeitshochdruckpumpe

Country Status (7)

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

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FR2794810B1 (fr) 1999-06-08 2001-08-31 Peugeot Citroen Automobiles Sa Pompe a haute pression perfectionnee
FR2794813B1 (fr) * 1999-06-08 2001-09-21 Peugeot Citroen Automobiles Sa Pompe a haute pression a bouchon de remplissage perfectionne
US6561771B2 (en) 2001-06-19 2003-05-13 Caterpillar Inc Axial piston pump with center inlet fill
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US20060168955A1 (en) * 2005-02-03 2006-08-03 Schlumberger Technology Corporation Apparatus for hydraulically energizing down hole mechanical systems
FR2883932B1 (fr) * 2005-04-04 2007-06-22 Siemens Automotive Hydraulics Perfectionnement aux pompes transfert
US7428812B2 (en) * 2006-05-04 2008-09-30 Fci Americas Technology, Inc. Hydraulic tool with wobble plate transmission
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US8122585B2 (en) * 2007-02-20 2012-02-28 Hubbell Incorporated Spanner plate
CN102979696B (zh) * 2012-12-03 2015-05-13 常州富邦电气有限公司 双进气高效气泵
US9909576B2 (en) 2015-01-23 2018-03-06 Caterpillar Inc. Pump drive system with hydraulic tappets
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Also Published As

Publication number Publication date
JP2000511989A (ja) 2000-09-12
US6264437B1 (en) 2001-07-24
ES2238968T3 (es) 2005-09-16
PT1048849E (pt) 2005-05-31
EP1048849B1 (de) 2005-03-16
DE69732802T2 (de) 2006-04-06
DE69732802D1 (de) 2005-04-21
EP1048849A1 (de) 2000-11-02
EP0901575A1 (de) 1999-03-17
WO1997047883A1 (fr) 1997-12-18
JP3990732B2 (ja) 2007-10-17

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