EP3059439A1 - Pump unit for a high-pressure pump - Google Patents

Pump unit for a high-pressure pump Download PDF

Info

Publication number
EP3059439A1
EP3059439A1 EP16157416.5A EP16157416A EP3059439A1 EP 3059439 A1 EP3059439 A1 EP 3059439A1 EP 16157416 A EP16157416 A EP 16157416A EP 3059439 A1 EP3059439 A1 EP 3059439A1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
working space
pressure
spring element
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.)
Granted
Application number
EP16157416.5A
Other languages
German (de)
French (fr)
Other versions
EP3059439B1 (en
Inventor
Michael Absmeier
Xaver GEBHARDT
Anatoliy Lyubar
Danica Siedenberg
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Automotive GmbH filed Critical Continental Automotive GmbH
Publication of EP3059439A1 publication Critical patent/EP3059439A1/en
Application granted granted Critical
Publication of EP3059439B1 publication Critical patent/EP3059439B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M59/022—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 having an accumulator storing pressurised fuel during pumping stroke of the piston for subsequent delivery to the injector
    • 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
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • 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
    • F02M59/22—Varying quantity or timing by adjusting cylinder-head space
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/447—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston means specially adapted to limit fuel delivery or to supply excess of fuel temporarily, e.g. for starting of the engine
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/023—Means for varying pressure in common rails
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • F02M63/0265—Pumps feeding common rails
    • 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
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/06—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means including spring- or weight-loaded lost-motion devices
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the invention relates to a pump unit for a high-pressure pump.
  • High-pressure pumps are regularly used to deliver fluid for a storage injection system for internal combustion engines of motor vehicles.
  • the high-pressure pump is intended to adapt an amount of fuel to be delivered to a consumption of the internal combustion engine at a corresponding load operating point.
  • the object of the invention is to provide a pump unit for a high-pressure pump, which makes it possible to adapt a quantity of a working medium to be conveyed to predetermined requirements.
  • the pump unit should be inexpensive to produce and have good energy efficiency.
  • the invention is characterized by a pump unit for a high-pressure pump.
  • the pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is released via the high-pressure outlet derived from the work space.
  • the pump unit comprises a pump piston channel formed in the pump housing with a longitudinal axis. Furthermore, the pump unit has a pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is coupled directly hydraulically to the working space.
  • the pump unit includes a balance piston directly hydraulically coupled to the working space and movably disposed in a balance piston passage along a second axis which is the longitudinal axis, the balance piston passage being disposed opposite to the pump piston passage along the longitudinal axis. Furthermore, the pump unit has a spring element which is mechanically coupled to an end of the compensating piston facing away from the working space and which is designed to influence a position of the compensating piston as a function of a force acting on the spring element. This allows a very flexible solution, since the spring element can be arranged instead of in the pump housing in other components of the high-pressure pump, for example in a pressure equalization vessel of the high-pressure pump.
  • the spring element and the compensation piston channel are combined with the low-pressure inlet and / or high-pressure outlet.
  • This has the advantage that, for example, already existing high-pressure pumps and / or high-pressure pump concepts can be retrofitted with such a compensation device, for example by replacing a low-pressure input module.
  • the spring element causes that in the delivery stroke of the pump piston on reaching the desired pressure in the working space of the balance piston is moved out of the working space, and so the volume of the working space remains substantially constant in the continuation of the course of the delivery stroke of the pump piston.
  • the balance piston comprises an inlet valve.
  • the invention is characterized by a pump unit for a high-pressure pump.
  • the pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is discharged from the working space via the high-pressure outlet.
  • the pump unit comprises a pump piston channel formed in the pump housing with a longitudinal axis.
  • the pump unit has a first pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is hydraulically coupled to the working space.
  • the pump unit has a second pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is coupled via a spring element to the first pump piston, wherein the spring element is formed, depending on a pressure in the working space a distance between the first and to adapt to the second pump piston.
  • the spring element is designed to leave the distance between the first and second pumping pistons substantially unchanged during a delivery stroke of the second pumping piston until a predetermined pressure in the working space is reached and to keep the pressure in the working space constant in the course of a continuation of the delivery stroke Adjust distance.
  • the spring element causes the first pump piston to essentially come to a standstill during the delivery stroke of the second pump piston when the desired pressure is reached in the working space and thus no further amount of the working fluid is conveyed into the working space.
  • the first pump piston and the second pump piston form a unit which is essentially in works the same way as a known from the prior art one-piece pump piston.
  • the invention is characterized by a pump unit for a high-pressure pump.
  • the pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is discharged from the working space via the high-pressure outlet.
  • the pump unit comprises a pump piston channel formed in the pump housing with a longitudinal axis.
  • the pump unit has a first pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is hydraulically coupled to the working space.
  • the pump unit has a second pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is hydraulically coupled to the first pump piston via a compensation volume, wherein the compensation volume is hydraulically coupled to a compensation unit, which is designed as a function of a pressure adjust the compensation volume in the working space.
  • the invention has the advantage that one between a Fuel tank and the pump unit separate electromagnetic flow control valve is not required and / or adjusting the volume flow of, for example, a current fuel consumption of the internal combustion engine by throttling an inlet flow and / or by driving off an unneeded, compressed fuel amount is not required. For example, by controlling the unnecessary amount of fuel with a pressure relief valve, the energy efficiency can deteriorate remarkably.
  • the compensation unit is designed to leave the compensating volume essentially unchanged during a delivery stroke of the second pump piston until a predetermined pressure in the working space is reached and to adjust the compensation volume in the course of a continuation of the delivery stroke in order to keep the pressure in the working space constant ,
  • the compensation unit has the effect that during a delivery stroke of the second pump piston when the desired pressure in the working space is reached, the first pump piston essentially comes to a standstill and thus no further quantity of the working fluid is conveyed into the working space.
  • the first pump piston and the second pump piston form a unit which operates in substantially the same way as a one-part pump piston known from the prior art.
  • the invention is characterized by a pump unit for a high-pressure pump.
  • the pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is discharged from the working space via the high-pressure outlet.
  • the pump unit comprises an in the pump housing formed pump piston channel with a longitudinal axis. Furthermore, the pump unit has a pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is coupled directly hydraulically to the working space.
  • the pump unit comprises a balancing piston which is directly hydraulically coupled to the working space and which is movably arranged in a balancing piston channel along a further axis. Furthermore, the pump unit has a spring element which is mechanically coupled to an end of the compensating piston facing away from the working space and which is designed to influence a position of the compensating piston as a function of a force acting on the spring element.
  • the balance piston comprises an inlet valve.
  • a pressure in the working space is limited by means of the compensating piston to a maximum value of approximately 250 bar.
  • the spring element has a spring characteristic with a degressive course.
  • the spring element may have a plate spring.
  • the spring element has a predetermined bias.
  • FIG. 6 shows a hydraulic diagram of a storage injection system 200 for internal combustion engines.
  • the accumulator injection system 200 has a prefeed pump 210 for delivering fuel from a fuel tank (not shown). Downstream of the feed pump 210, a filter and damping unit 212 is arranged. Downstream of the feed pump 210 and the filter and damping unit 212, a high-pressure pump 214 with at least one pump unit 10 is further arranged.
  • the pump unit 10 has an inlet valve 216 and an outlet valve 218.
  • the inlet valve 216 is preferably designed as a digital inlet valve, by means of which the volume flow is controlled at the inlet of the pump unit 10.
  • the high-pressure pump 214 the fuel is conveyed to a fuel reservoir 220 in order to get from there to (not shown) injection valves.
  • FIG. 1 shows a first embodiment of the pump unit 10 of the high-pressure pump 214.
  • the high-pressure pump 214 may be formed, for example, as a radial piston pump.
  • the high pressure pump 214 may be provided for fueling a high pressure accumulator injection system, such as a common rail injection system.
  • the pump unit 10 comprises a pump housing 15 with a low-pressure inlet 17 and a high-pressure outlet 19.
  • the low-pressure inlet 17 has, for example, a feed line. which is preferably hydraulically coupled to the working space 20 by means of an inlet valve.
  • the inlet valve serves to prevent a backflow into the supply line, in particular when filling and compressing the working medium.
  • the high-pressure outlet 19 has a drain line and an outlet valve which is preferably arranged in this outlet.
  • the outlet valve is formed, for example, as a high-pressure valve, which allows only from a predetermined fluid pressure in the working chamber 20, an ejection of the working fluid from the working space 20 in the drain line.
  • the exhaust valve prevents a backflow of the working medium, for example from a rail, in the pump unit 10th
  • the pump unit 10 further comprises a pump piston 30, which is arranged in a pump piston channel 36 formed in the pump housing 15.
  • the pump piston channel 36 has a longitudinal axis L1 along which the pump piston 30 is movably arranged.
  • the pump piston 30 is hydraulically coupled directly to the working space 20.
  • the working medium for example the fuel
  • the working medium located in the working space 20 is compressed or discharged via the outlet valve under high pressure to the discharge line, the inlet valve being closed.
  • the pump unit 10 on a balance piston 40.
  • the balance piston 40 is arranged in a balance piston channel 45.
  • the compensation channel has a second axis A2 along which the compensating piston 40 is movably arranged in the compensation channel.
  • the compensating piston 40 is likewise directly hydraulically coupled to the working space 20.
  • the pump unit 10 comprises a spring element 50.
  • the spring element 50 is mechanically coupled to the first end of the compensating piston 40 facing away from the working space 20.
  • the spring element 50 is formed, depending on a force acting on the spring element 50, a position of the balance piston 40 to influence.
  • the spring element 50 may in this case have, for example, a degressive spring characteristic.
  • the balance piston 40 starts a movement only when the pressure in the working space 20 exceeds a predetermined value.
  • this predetermined pressure in the working space 20 is about 245 bar.
  • the balance piston 40 stops its movement as soon as the pressure in the working space 20 exceeds another predetermined value.
  • this further predetermined pressure in the working space 20 is about 258 bar. It can thus be achieved that at a pressure in the working chamber 20 of about 245 bar, the compensating piston 40 compensates for the change in volume in the working space 20 by the pump piston 30, and so a further increase in pressure in the working space 20 can be avoided.
  • the pressure in the working chamber 20 can be limited by means of the balancing piston 40 to a value of about 245 bar. This is especially shown in FIG. 7 with a schematic view of the functional dependence of the stroke of the balance piston 40 of the pump unit 10 of the pressure in the working space 20th
  • FIG. 8a the pressure curves at the outlet of the pump unit 10 ( FIG. 8a ) and in the fuel tank 220 ( FIG. 8b ) as well as injector injection quantities as a function of a rotational speed of the pump unit 10 (FIG. FIG. 8c ).
  • the pressure at the outlet of the pump unit 10 by means of the balance piston 40 in particular at higher speeds (here from about 4,800) can be limited to a value of about 245 bar (see boundary G between the dark and the lighter area).
  • the compensating piston 40 may for example be arranged in the pump housing 15 such that the longitudinal axis L1 of the pump piston channel 36 and the second axis A2 include a predetermined angle.
  • the compensating piston channel 45 can also be arranged opposite the pump piston channel 36 along the longitudinal axis L1.
  • the spring element 50 can be arranged, for example, in a further vessel 60 of the pump unit 10. In the vessel 60, the spring element 50 may be arranged such that the spring element 50 has a bias voltage.
  • FIG. 2 shows a second embodiment of the pump unit 10, in which the spring element 50 is arranged in a pressure equalization vessel 60 '.
  • the spring element 50 can additionally be used to dampen pressure pulsations. This is in the in FIG. 2 shown embodiment between the balance piston 40 and the spring element 50, a movable member 70, for example, a rolling diaphragm, clamped.
  • FIG. 3 shows a third embodiment of the pump unit 10, wherein the pump unit 10 has a combined arrangement of the balance piston 40 and the inlet valve.
  • the balance piston 40 may include the inlet valve.
  • FIG. 4 shows a fourth embodiment of the pump unit 10.
  • the pump unit 10 has a first pump piston 32 and a second pump piston 34.
  • the first pump piston 32 is movably arranged in the pump piston channel 36 along the longitudinal axis L1 and directly hydraulically coupled to the working space 20.
  • the second pump piston 34 is also movably arranged in the pump piston channel 36 along the longitudinal axis L1 and is coupled via the spring element 50 with the first Pumping piston 32, wherein the spring element 50 is formed, depending on a pressure in the working space 20 to adjust a distance between the first 32 and the second pump piston 34.
  • the spring element 50 is designed to leave the distance between the first 32 and second pump piston 34 substantially unchanged during a delivery stroke of the second pump piston 34 until a predetermined pressure in the working space 20 is reached, and to keep the pressure in the working space 20 constant in the process Course of a continuation of the delivery stroke of the second pump piston 34 to adjust the distance.
  • the first pumping piston 32 has a recess 90 at a first end facing the second pumping piston 34. In the recess 90, the spring element 50 is arranged. Alternatively, the spring element may be arranged outside of the first pump piston.
  • the second pump piston 34 has a plunger 80 at a first end facing the first pump piston 32. The plunger 80 is mechanically coupled to the spring element 50.
  • FIG. 5 shows a fifth embodiment of the pump unit 10.
  • the second pump piston 34 is hydraulically coupled to the first pump piston 32 via a compensation volume 100, wherein the compensation volume 100 is hydraulically coupled to a compensation unit 110, which is designed to adjust the compensation volume 100 depending on a pressure in the working space 20.
  • the compensation unit 110 is formed, for example, at a delivery stroke of the pump piston until reaching a predetermined pressure in the working chamber 20 to leave the compensation volume 100 substantially unchanged and in the sense of keeping the pressure in the working chamber 20 constant in the course of a continuation of the delivery stroke, the compensation volume 100.
  • the compensation unit 110 includes, for example, a compensation chamber 120, which is arranged in the pump housing 15.
  • the compensation chamber has an opening, via which the compensation chamber is hydraulically coupled without resistance to a pump inlet.
  • the compensation unit 110 comprises a further spring element 50 ', which is arranged in the compensation chamber 120.
  • the compensation unit 110 further comprises a piston 130, which is arranged movably in the compensation chamber 120 along a third axis.
  • the piston is mechanically coupled at a first end to the further spring element 50 'and at a second end directly hydraulically coupled to the working volume.
  • the further spring element 50 ' may have a spring characteristic with a degressive course. Further, the further spring element 50 'may be arranged and configured such that it has a predetermined bias voltage.

Abstract

Pumpeneinheit (10) für eine Hochdruckpumpe, umfassend: - ein Pumpengehäuse (15), das einen Niederdruckeingang (17) aufweist, über den einem im dem Pumpengehäuse (15) ausgebildeten Arbeitsraum (20) ein Arbeitsmedium zugeführt wird, und einen Hochdruckausgang (19), über den das Arbeitsmedium aus dem Arbeitsraum (20) abgeleitet wird, - einen in dem Pumpengehäuse (15) ausgebildeter Pumpkolbenkanal (36) mit einer Längsachse (L1), - einen Pumpenkolben, der entlang der Längsachse (L1) beweglich in dem Pumpkolbenkanal (36) angeordnet ist und der direkt hydraulisch mit dem Arbeitsraum (20) gekoppelt ist, - einen Ausgleichskolben (40), der direkt hydraulisch mit dem Arbeitsraum (20) gekoppelt ist und der in einem Ausgleichskolbenkanal (45) mit einer weiteren Achse (A3) beweglich angeordnet ist, und - ein Federelement (50), das an einem dem Arbeitsraum (20) abgewandten Ende des Ausgleichskolbens (40) mit diesem mechanisch gekoppelt ist und ausgebildet ist, abhängig von einer Kraft, die auf das Federelement (50) wirkt, eine Position des Ausgleichskolbens (40) zu beeinflussen, wobei der Ausgleichskolben (40) ein Einlassventil umfasst.Pump unit (10) for a high-pressure pump, comprising: - A pump housing (15) having a low pressure input (17), via which a in the pump housing (15) formed working space (20) is supplied to a working medium, and a high-pressure outlet (19) through which the working fluid from the working space (20 ) is derived, a pump piston channel (36) formed in the pump housing (15) with a longitudinal axis (L1), a pump piston which is arranged movably in the pump piston channel along the longitudinal axis and which is directly hydraulically coupled to the working space, - A compensating piston (40) which is directly hydraulically coupled to the working space (20) and which is arranged in a compensating piston channel (45) with a further axis (A3) movable, and a spring element (50) which is mechanically coupled to an end of the compensating piston (40) facing away from the working space (20) and is designed, depending on a force acting on the spring element (50), a position of the compensating piston ( 40), wherein the compensating piston (40) comprises an inlet valve.

Description

Die Erfindung betrifft eine Pumpeneinheit für eine Hochdruckpumpe.The invention relates to a pump unit for a high-pressure pump.

Hochdruckpumpen werden regelmäßig zur Förderung von Fluid für ein Speichereinspritzsystem für Brennkraftmaschinen von Kraftfahrzeugen verwendet. Speichereinspritzsysteme für Brennkraftmaschinen von Kraftfahrzeugen, so zum Beispiel in Common-Rail-Systemen, sollen den notwendigen Volumenstrom und den erforderlichen Fluiddruck bereitstellen können. Die Hochdruckpumpe soll eine zu fördernde Brennkraftstoffmenge einem Verbrauch der Brennkraftmaschine bei einem entsprechenden Lastarbeitspunkt anpassen.High-pressure pumps are regularly used to deliver fluid for a storage injection system for internal combustion engines of motor vehicles. Storage injection systems for internal combustion engines of motor vehicles, for example in common rail systems, should be able to provide the necessary volume flow and the required fluid pressure. The high-pressure pump is intended to adapt an amount of fuel to be delivered to a consumption of the internal combustion engine at a corresponding load operating point.

Die Aufgabe der Erfindung ist es, eine Pumpeneinheit für eine Hochdruckpumpe zu schaffen, die ermöglicht, eine Menge eines zu fördernden Arbeitsmediums an vorgegebene Anforderungen anzupassen. Zugleich soll die Pumpeneinheit kostengünstig herstellbar sein und einen guten energetischen Wirkungsgrad aufweisen.The object of the invention is to provide a pump unit for a high-pressure pump, which makes it possible to adapt a quantity of a working medium to be conveyed to predetermined requirements. At the same time, the pump unit should be inexpensive to produce and have good energy efficiency.

Die Aufgabe wird gelöst durch die Merkmale der unabhängigen Patentansprüche. Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen gekennzeichnet.The object is solved by the features of the independent claims. Advantageous embodiments of the invention are characterized in the subclaims.

Gemäß einem ersten Aspekt zeichnet sich die Erfindung aus durch eine Pumpeneinheit für eine Hochdruckpumpe. Die Pumpeneinheit umfasst ein Pumpengehäuse mit einem Niederdruckeingang und einem Hochdruckausgang. Über den Niederdruckeingang wird einem in dem Pumpengehäuse ausgebildeten Arbeitsraum ein Arbeitsmedium zugeführt. Über den Hochdruckausgang wird das Arbeitsmedium aus dem Arbeitsraum abgeleitet. Die Pumpeneinheit umfasst einen in dem Pumpengehäuse ausgebildeten Pumpkolbenkanal mit einer Längsachse. Ferner weist die Pumpeneinheit einen Pumpkolben auf, der entlang der Längsachse beweglich in dem Pumpkolbenkanal angeordnet ist und der direkt hydraulisch mit dem Arbeitsraum gekoppelt ist. Die Pumpeneinheit umfasst einen Ausgleichskolben, der direkt hydraulisch mit dem Arbeitsraum gekoppelt ist und der in einem Ausgleichskolbenkanal entlang einer zweiten Achse, die die Längsachse ist, beweglich angeordnet ist, wobei der Ausgleichskolbenkanal gegenüber dem Pumpkolbenkanal entlang der Längsachse angeordnet ist. Des Weiteren weist die Pumpeneinheit ein Federelement auf, das an einem dem Arbeitsraum abgewandten Ende des Ausgleichskolbens mit diesem mechanisch gekoppelt ist und das ausgebildet ist, abhängig von einer Kraft, die auf das Federelement wirkt, eine Position des Ausgleichskolbens zu beeinflussen. Dies ermöglicht eine sehr flexible Lösung, da das Federelement anstatt in dem Pumpengehäuse in weiteren Komponenten der Hochdruckpumpe, beispielsweise in einem Druckausgleichsgefäß der Hochdruckpumpe, angeordnet werden kann. Beispielsweise ist auch möglich, dass das Federelement und der Ausgleichskolbenkanal mit dem Niederdruckeingang und/oder Hochdruckausgang kombiniert angeordnet werden. Dies hat den Vorteil, dass beispielsweise bereits existierende Hochdruckpumpen und/oder Hochdruckpumpenkonzepte nachträglich mit solch einer Ausgleichsvorrichtung ausgestattet werden können, beispielsweise durch einen Austausch einer Niederdruckeingangsbaugruppe. Vorteilhafterweise bewirkt das Federelement, dass bei dem Förderhub des Pumpkolbens bei Erreichen des gewünschten Drucks im Arbeitsraum der Ausgleichskolben aus dem Arbeitsraum heraus bewegt wird, und so bei der Fortsetzung des Verlaufs des Förderhubs des Pumpkolben das Volumen des Arbeitsraums im Wesentlichen konstant bleibt.According to a first aspect, the invention is characterized by a pump unit for a high-pressure pump. The pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is released via the high-pressure outlet derived from the work space. The pump unit comprises a pump piston channel formed in the pump housing with a longitudinal axis. Furthermore, the pump unit has a pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is coupled directly hydraulically to the working space. The pump unit includes a balance piston directly hydraulically coupled to the working space and movably disposed in a balance piston passage along a second axis which is the longitudinal axis, the balance piston passage being disposed opposite to the pump piston passage along the longitudinal axis. Furthermore, the pump unit has a spring element which is mechanically coupled to an end of the compensating piston facing away from the working space and which is designed to influence a position of the compensating piston as a function of a force acting on the spring element. This allows a very flexible solution, since the spring element can be arranged instead of in the pump housing in other components of the high-pressure pump, for example in a pressure equalization vessel of the high-pressure pump. For example, it is also possible that the spring element and the compensation piston channel are combined with the low-pressure inlet and / or high-pressure outlet. This has the advantage that, for example, already existing high-pressure pumps and / or high-pressure pump concepts can be retrofitted with such a compensation device, for example by replacing a low-pressure input module. Advantageously, the spring element causes that in the delivery stroke of the pump piston on reaching the desired pressure in the working space of the balance piston is moved out of the working space, and so the volume of the working space remains substantially constant in the continuation of the course of the delivery stroke of the pump piston.

In einer vorteilhaften Ausgestaltung der Erfindung gemäß dem dritten Aspekt umfasst der Ausgleichskolben ein Einlassventil.In an advantageous embodiment of the invention according to the third aspect, the balance piston comprises an inlet valve.

Gemäß einem zweiten Aspekt zeichnet sich die Erfindung aus durch eine Pumpeneinheit für eine Hochdruckpumpe. Die Pumpeneinheit umfasst ein Pumpengehäuse mit einem Niederdruckeingang und einem Hochdruckausgang. Über den Niederdruckeingang wird einem in dem Pumpengehäuse ausgebildeten Arbeitsraum ein Arbeitsmedium zugeführt. Über den Hochdruckausgang wird das Arbeitsmedium aus dem Arbeitsraum abgeleitet. Ferner umfasst die Pumpeneinheit einen in dem Pumpengehäuse ausgebildeten Pumpkolbenkanal mit einer Längsachse. Die Pumpeneinheit weist einen ersten Pumpkolben auf, der in dem Pumpkolbenkanal entlang der Längsachse beweglich angeordnet ist und der hydraulisch gekoppelt ist mit dem Arbeitsraum. Ferner weist die Pumpeneinheit einen zweiten Pumpkolben auf, der in dem Pumpkolbenkanal entlang der Längsachse beweglich angeordnet ist und der über ein Federelement gekoppelt ist mit dem ersten Pumpkolben, wobei das Federelement ausgebildet ist, abhängig von einem Druck in den Arbeitsraum einen Abstand zwischen dem ersten und dem zweiten Pumpkolben anzupassen. Das Federelement ist ausgebildet, bei einem Förderhub des zweiten Pumpkolbens bis zum Erreichen eines vorgegebenen Drucks in dem Arbeitsraum den Abstand zwischen dem ersten und zweiten Pumpkolben im Wesentlichen unverändert zu lassen und im Sinne eines Konstanthaltens des Drucks in dem Arbeitsraum im Verlauf einer Fortsetzung des Förderhubs den Abstand anzupassen.According to a second aspect, the invention is characterized by a pump unit for a high-pressure pump. The pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is discharged from the working space via the high-pressure outlet. Furthermore, the pump unit comprises a pump piston channel formed in the pump housing with a longitudinal axis. The pump unit has a first pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is hydraulically coupled to the working space. Furthermore, the pump unit has a second pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is coupled via a spring element to the first pump piston, wherein the spring element is formed, depending on a pressure in the working space a distance between the first and to adapt to the second pump piston. The spring element is designed to leave the distance between the first and second pumping pistons substantially unchanged during a delivery stroke of the second pumping piston until a predetermined pressure in the working space is reached and to keep the pressure in the working space constant in the course of a continuation of the delivery stroke Adjust distance.

Vorteilhafterweise bewirkt das Federelement, dass bei dem Förderhub des zweiten Pumpkolbens bei Erreichen des gewünschten Drucks im Arbeitsraum der erste Pumpkolben im Wesentlichen zum Stillstand kommt und somit keine weitere Menge des Arbeitsmittels in den Arbeitsraum gefördert wird. Bis zum Erreichen des gewünschten Drucks in dem Arbeitsraum bilden der erste Pumpkolben und der zweite Pumpkolben eine Einheit, die im Wesentlichen in gleicher Weise arbeitet wie ein aus dem Stand der Technik bekannter einteiliger Pumpkolben.Advantageously, the spring element causes the first pump piston to essentially come to a standstill during the delivery stroke of the second pump piston when the desired pressure is reached in the working space and thus no further amount of the working fluid is conveyed into the working space. Until the desired pressure in the working space has been reached, the first pump piston and the second pump piston form a unit which is essentially in works the same way as a known from the prior art one-piece pump piston.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung gemäß dem ersten und zweiten Aspekt ist der Druck in dem Arbeitsraum mittels des zweiten Pumpkolbens auf einen Wert von maximal ca. 250 bar begrenzt.In a further advantageous embodiment of the invention according to the first and second aspects of the pressure in the working space by means of the second pump piston is limited to a maximum value of about 250 bar.

Gemäß einem dritten Aspekt zeichnet sich die Erfindung aus durch eine Pumpeneinheit für eine Hochdruckpumpe. Die Pumpeneinheit umfasst ein Pumpengehäuse mit einem Niederdruckeingang und einem Hochdruckausgang. Über den Niederdruckeingang wird einem in dem Pumpengehäuse ausgebildeten Arbeitsraum ein Arbeitsmedium zugeführt. Über den Hochdruckausgang wird das Arbeitsmedium aus dem Arbeitsraum abgeleitet. Des Weiteren umfasst die Pumpeneinheit einen in dem Pumpengehäuse ausgebildeten Pumpkolbenkanal mit einer Längsachse. Die Pumpeneinheit weist einen ersten Pumpkolben auf, der in dem Pumpkolbenkanal entlang der Längsachse beweglich angeordnet ist und der hydraulisch gekoppelt ist mit dem Arbeitsraum. Ferner weist die Pumpeneinheit einen zweiten Pumpkolben auf, der in dem Pumpkolbenkanal entlang der Längsachse beweglich angeordnet ist und der über ein Ausgleichsvolumen hydraulisch gekoppelt ist mit dem ersten Pumpkolben, wobei das Ausgleichsvolumen hydraulisch gekoppelt ist mit einer Ausgleichseinheit, die ausgebildet ist, abhängig von einem Druck in dem Arbeitsraum das Ausgleichsvolumen anzupassen.According to a third aspect, the invention is characterized by a pump unit for a high-pressure pump. The pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is discharged from the working space via the high-pressure outlet. Furthermore, the pump unit comprises a pump piston channel formed in the pump housing with a longitudinal axis. The pump unit has a first pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is hydraulically coupled to the working space. Furthermore, the pump unit has a second pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is hydraulically coupled to the first pump piston via a compensation volume, wherein the compensation volume is hydraulically coupled to a compensation unit, which is designed as a function of a pressure adjust the compensation volume in the working space.

Dies ermöglicht vorteilhafterweise eine Regelung des Volumenstroms des Arbeitsmediums, vorzugsweise eines Kraftstoffes, mit einer reduzierten Anzahl von Bauteilen und kann einen Beitrag leisten dazu, dass die Pumpeneinheit und somit die Hochdruckpumpe einen guten energetischen Wirkungsgrad aufweisen kann. Die Einsparung von Bauteilen ermöglicht eine kostengünstige Herstellung. Die Erfindung hat den Vorteil, dass ein zwischen einem Kraftstofftank und der Pumpeneinheit gesondertes elektromagnetisches Volumenstromregelventil nicht erforderlich ist und/oder ein Anpassen des Volumenstroms an beispielsweise einen aktuellen Brennkraftstoffverbrauchs der Brennkraftmaschine durch Drosseln eines Zulaufstroms und/oder durch Absteuern einer nicht benötigten, verdichteten Kraftstoffmenge nicht erforderlich ist. Beispielsweise kann sich durch ein Absteuern der nicht benötigten Kraftstoffmenge mit einem Druckbegrenzungsventil der energetische Wirkungsgrad bemerkenswert verschlechtern.This advantageously makes it possible to control the volume flow of the working medium, preferably a fuel, with a reduced number of components and can contribute to the pump unit and thus the high-pressure pump having good energy efficiency. The saving of components enables cost-effective production. The invention has the advantage that one between a Fuel tank and the pump unit separate electromagnetic flow control valve is not required and / or adjusting the volume flow of, for example, a current fuel consumption of the internal combustion engine by throttling an inlet flow and / or by driving off an unneeded, compressed fuel amount is not required. For example, by controlling the unnecessary amount of fuel with a pressure relief valve, the energy efficiency can deteriorate remarkably.

In einer vorteilhaften Ausgestaltung ist die Ausgleichseinheit ausgebildet, bei einem Förderhub des zweiten Pumpkolbens bis zum Erreichen eines vorgegebenen Drucks in dem Arbeitsraum das Ausgleichsvolumen im Wesentlichen unverändert zu lassen und im Sinne eines Konstanthaltens des Drucks in dem Arbeitsraum im Verlauf einer Fortsetzung des Förderhubs das Ausgleichsvolumen anzupassen. Die Ausgleichseinheit bewirkt, dass bei einem Förderhub des zweiten Pumpkolbens bei Erreichen des gewünschten Drucks im Arbeitsraum der erste Pumpkolben im Wesentlichen zum Stillstand kommt und somit keine weitere Menge des Arbeitsmittels in den Arbeitsraum gefördert wird. Bis zum Erreichen des gewünschten Drucks in dem Arbeitsraum bilden der erste Pumpkolben und der zweite Pumpkolben eine Einheit, die im Wesentlichen in gleicher Weise arbeitet wie ein aus dem Stand der Technik bekannter einteiliger Pumpkolben.In an advantageous embodiment, the compensation unit is designed to leave the compensating volume essentially unchanged during a delivery stroke of the second pump piston until a predetermined pressure in the working space is reached and to adjust the compensation volume in the course of a continuation of the delivery stroke in order to keep the pressure in the working space constant , The compensation unit has the effect that during a delivery stroke of the second pump piston when the desired pressure in the working space is reached, the first pump piston essentially comes to a standstill and thus no further quantity of the working fluid is conveyed into the working space. Until the desired pressure is reached in the working space, the first pump piston and the second pump piston form a unit which operates in substantially the same way as a one-part pump piston known from the prior art.

Gemäß einem vierten Aspekt zeichnet sich die Erfindung aus durch eine Pumpeneinheit für eine Hochdruckpumpe. Die Pumpeneinheit umfasst ein Pumpengehäuse mit einem Niederdruckeingang und einem Hochdruckausgang. Über den Niederdruckeingang wird einem in dem Pumpengehäuse ausgebildeten Arbeitsraum ein Arbeitsmedium zugeführt. Über den Hochdruckausgang wird das Arbeitsmedium aus dem Arbeitsraum abgeleitet. Die Pumpeneinheit umfasst einen in dem Pumpengehäuse ausgebildeten Pumpkolbenkanal mit einer Längsachse. Ferner weist die Pumpeneinheit einen Pumpkolben auf, der entlang der Längsachse beweglich in dem Pumpkolbenkanal angeordnet ist und der direkt hydraulisch mit dem Arbeitsraum gekoppelt ist. Die Pumpeneinheit umfasst einen Ausgleichskolben, der direkt hydraulisch mit dem Arbeitsraum gekoppelt ist und der in einem Ausgleichskolbenkanal entlang einer weiteren Achse beweglich angeordnet ist. Des Weiteren weist die Pumpeneinheit ein Federelement auf, das an einem dem Arbeitsraum abgewandten Ende des Ausgleichskolbens mit diesem mechanisch gekoppelt ist und das ausgebildet ist, abhängig von einer Kraft, die auf das Federelement wirkt, eine Position des Ausgleichskolbens zu beeinflussen. Der Ausgleichskolben umfasst ein Einlassventil.According to a fourth aspect, the invention is characterized by a pump unit for a high-pressure pump. The pump unit includes a pump housing with a low pressure inlet and a high pressure outlet. Via the low-pressure inlet, a working medium is supplied to a working space formed in the pump housing. The working medium is discharged from the working space via the high-pressure outlet. The pump unit comprises an in the pump housing formed pump piston channel with a longitudinal axis. Furthermore, the pump unit has a pump piston, which is arranged movably in the pump piston channel along the longitudinal axis and which is coupled directly hydraulically to the working space. The pump unit comprises a balancing piston which is directly hydraulically coupled to the working space and which is movably arranged in a balancing piston channel along a further axis. Furthermore, the pump unit has a spring element which is mechanically coupled to an end of the compensating piston facing away from the working space and which is designed to influence a position of the compensating piston as a function of a force acting on the spring element. The balance piston comprises an inlet valve.

In einer vorteilhaften Ausgestaltung der Erfindung gemäß dem dritten und vierten Aspekt ist ein Druck in dem Arbeitsraum mittels des Ausgleichskolbens auf einen Wert von maximal ca. 250 bar begrenzt.In an advantageous embodiment of the invention according to the third and fourth aspects, a pressure in the working space is limited by means of the compensating piston to a maximum value of approximately 250 bar.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung gemäß dem ersten, zweiten, dritten und vierten Aspekt weist das Federelement eine Federkennlinie mit einem degressiven Verlauf auf. Beispielsweise kann das Federelement eine Tellerfeder aufweisen.In a further advantageous embodiment of the invention according to the first, second, third and fourth aspects, the spring element has a spring characteristic with a degressive course. For example, the spring element may have a plate spring.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung gemäß dem ersten, zweiten, dritten und vierten Aspekt weist das Federelement eine vorgegebene Vorspannung auf.In a further advantageous embodiment of the invention according to the first, second, third and fourth aspects, the spring element has a predetermined bias.

Ausführungsbeispiele der Erfindung sind im Folgenden anhand der schematischen Zeichnungen erläutert.Embodiments of the invention are explained below with reference to the schematic drawings.

Es zeigen:

Figur 1
eine schematische Ansicht eines ersten Ausführungsbeispiels einer Pumpeneinheit,
Figur 2
eine schematische Ansicht eines zweiten Ausführungsbeispiels der Pumpeneinheit,
Figur 3
eine schematische Ansicht eines dritten Ausführungsbeispiels der Pumpeneinheit,
Figur 4
eine schematische Ansicht eines vierten Ausführungsbeispiels der Pumpeneinheit,
Figur 5
eine schematische Ansicht eines fünften Ausführungsbeispiels der Pumpeneinheit,
Figur 6
eine schematische Ansicht eines Speichereinspritzsystems mit der Pumpeneinheit,
Figur 7
eine schematische Ansicht der funktionalen Abhängigkeit des Hubs eines Ausgleichskolbens der Pumpeneinheit von einem Druck der Pumpeneinheit, und
Figuren 8a, 8b und 8c
Darstellungen des Drucks und der Einspritzmenge der Pumpeneinheit in Abhängigkeit von einer Drehzahl der Pumpeneinheit.
Show it:
FIG. 1
a schematic view of a first embodiment of a pump unit,
FIG. 2
a schematic view of a second embodiment of the pump unit,
FIG. 3
a schematic view of a third embodiment of the pump unit,
FIG. 4
a schematic view of a fourth embodiment of the pump unit,
FIG. 5
a schematic view of a fifth embodiment of the pump unit,
FIG. 6
a schematic view of a storage injection system with the pump unit,
FIG. 7
a schematic view of the functional dependence of the stroke of a balance piston of the pump unit of a pressure of the pump unit, and
Figures 8a, 8b and 8c
Representations of the pressure and the injection quantity of the pump unit in dependence on a rotational speed of the pump unit.

Figur 6 zeigt ein Hydraulikschema eines Speichereinspritzsystems 200 für Brennkraftmaschinen. Das Speichereinspritzsystem 200 hat eine Vorförderpumpe 210 zur Förderung von Kraftstoff aus einem (nicht dargestellten) Kraftstofftank. Stromabwärts der Vorförderpumpe 210 ist eine Filter- und Dämpfungseinheit 212 angeordnet. Stromabwärts der Vorförderpumpe 210 und der Filter- und Dämpfungseinheit 212 ist weiter eine Hochdruckpumpe 214 mit mindestens einer Pumpeneinheit 10 angeordnet. Die Pumpeneinheit 10 hat ein Einlassventil 216 und ein Auslassventil 218. Das Einlassventil 216 ist vorzugsweise als digitales Einlassventil ausgebildet, mittels der der Volumenstrom eingangs der Pumpeneinheit 10 geregelt wird. Mittels der Hochdruckpumpe 214 wird der Kraftstoff in einen Kraftstoffspeicher 220 gefördert, um von dort zu (nicht dargestellten) Einspritzventilen zu gelangen. FIG. 6 shows a hydraulic diagram of a storage injection system 200 for internal combustion engines. The accumulator injection system 200 has a prefeed pump 210 for delivering fuel from a fuel tank (not shown). Downstream of the feed pump 210, a filter and damping unit 212 is arranged. Downstream of the feed pump 210 and the filter and damping unit 212, a high-pressure pump 214 with at least one pump unit 10 is further arranged. The pump unit 10 has an inlet valve 216 and an outlet valve 218. The inlet valve 216 is preferably designed as a digital inlet valve, by means of which the volume flow is controlled at the inlet of the pump unit 10. By means of the high-pressure pump 214, the fuel is conveyed to a fuel reservoir 220 in order to get from there to (not shown) injection valves.

Figur 1 zeigt ein erstes Ausführungsbeispiel der Pumpeneinheit 10 der Hochdruckpumpe 214. Die Hochdruckpumpe 214 kann beispielsweise als Radialkolbenpumpe ausgebildet sein. Zum Beispiel kann die Hochdruckpumpe 214 zur Kraftstoffversorgung bei einem Hochdruckspeichereinspritzsystem, wie zum Beispiel bei einem Common-Rail-Einspritzsystem, vorgesehen sein. FIG. 1 shows a first embodiment of the pump unit 10 of the high-pressure pump 214. The high-pressure pump 214 may be formed, for example, as a radial piston pump. For example, the high pressure pump 214 may be provided for fueling a high pressure accumulator injection system, such as a common rail injection system.

Die Pumpeneinheit 10 umfasst ein Pumpengehäuse 15 mit einem Niederdruckeingang 17 und einem Hochdruckausgang 19. Um einen Arbeitsraum 20, der in dem Pumpengehäuse 15 angeordnet ist, mit einem Arbeitsmedium, insbesondere einem Fluid, befüllen zu können, weist der Niederdruckeingang 17 beispielsweise eine Zuleitung auf, die vorzugsweise mit dem Arbeitsraum 20 mittels eines Einlassventils hydraulisch gekoppelt ist. Das Einlassventil dient dazu, insbesondere beim Befüllen und Komprimieren des Arbeitsmediums ein Zurückströmen in die Zulaufleitung zu verhindern.The pump unit 10 comprises a pump housing 15 with a low-pressure inlet 17 and a high-pressure outlet 19. In order to be able to fill a working space 20, which is arranged in the pump housing 15, with a working medium, in particular a fluid, the low-pressure inlet 17 has, for example, a feed line. which is preferably hydraulically coupled to the working space 20 by means of an inlet valve. The inlet valve serves to prevent a backflow into the supply line, in particular when filling and compressing the working medium.

Der Hochdruckausgang 19 weist eine Ablaufleitung und ein vorzugsweise in dieser angeordneten Auslassventil auf. Das Auslassventil ist beispielsweise als Hochdruckventil ausgebildet, das erst ab einem vorgegebenen Fluiddruck in dem Arbeitsraum 20 einen Ausstoß des Arbeitsmediums aus dem Arbeitsraum 20 in die Ablaufleitung ermöglicht. Das Auslassventil verhindert ein Zurückströmen des Arbeitsmediums, beispielsweise aus einem Rail, in die Pumpeneinheit 10.The high-pressure outlet 19 has a drain line and an outlet valve which is preferably arranged in this outlet. The outlet valve is formed, for example, as a high-pressure valve, which allows only from a predetermined fluid pressure in the working chamber 20, an ejection of the working fluid from the working space 20 in the drain line. The exhaust valve prevents a backflow of the working medium, for example from a rail, in the pump unit 10th

Die Pumpeneinheit 10 umfasst ferner einen Pumpenkolben 30, der in einem in dem Pumpengehäuse 15 ausgebildeten Pumpkolbenkanal 36 angeordnet ist. Der Pumpkolbenkanal 36 weist eine Längsachse L1 auf entlang der Pumpkolben 30 beweglich angeordnet ist. Der Pumpkolben 30 ist hydraulisch direkt gekoppelt mit dem Arbeitsraum 20.The pump unit 10 further comprises a pump piston 30, which is arranged in a pump piston channel 36 formed in the pump housing 15. The pump piston channel 36 has a longitudinal axis L1 along which the pump piston 30 is movably arranged. The pump piston 30 is hydraulically coupled directly to the working space 20.

Während eines Saughubs, das heißt während einer von dem Arbeitsraum 20 weg gerichteten Bewegung des Pumpkolbens 30, wird das Arbeitsmedium, beispielsweise der Kraftstoff, aus der Zulaufleitung über das Einlassventil in den Arbeitsraum 20 gefördert, wobei das Auslassventil geschlossen ist. Während eines Förderhubs, das heißt während einer zu dem Arbeitsraum 20 hin gerichteten Bewegung des Pumpkolbens 30, wird das in dem Arbeitsraum 20 befindliche Arbeitsmedium komprimiert beziehungsweise über das Auslassventil unter hohem Druck an die Ablaufleitung abgegeben, wobei das Einlassventil geschlossen ist.During a suction stroke, that is to say during a movement of the pumping piston 30 away from the working space 20, the working medium, for example the fuel, is conveyed from the supply line via the inlet valve into the working space 20, the outlet valve being closed. During a delivery stroke, that is to say during a movement of the pump piston 30 directed toward the working space 20, the working medium located in the working space 20 is compressed or discharged via the outlet valve under high pressure to the discharge line, the inlet valve being closed.

Bei dem in Figur 1 gezeigten Ausführungsbeispiel der Pumpeneinheit 10 weist die Pumpeneinheit 10 einen Ausgleichskolben 40 auf. Der Ausgleichskolben 40 ist in einem Ausgleichskolbenkanal 45 angeordnet. Der Ausgleichskanal weist eine zweite Achse A2 auf entlang derer der Ausgleichskolben 40 in den Ausgleichskanal beweglich angeordnet ist. Der Ausgleichskolben 40 ist ebenfalls direkt hydraulisch gekoppelt mit dem Arbeitsraum 20. Des Weiteren umfasst die Pumpeneinheit 10 ein Federelement 50. Das Federelement 50 ist an einem von dem Arbeitsraum 20 abgewandten ersten Ende des Ausgleichskolbens 40 mit diesem mechanisch gekoppelt. Das Federelement 50 ist ausgebildet, abhängig von einer auf das Federelement 50 wirkenden Kraft eine Position des Ausgleichskolbens 40 zu beeinflussen. Das Federelement 50 kann hierbei beispielsweise eine degressive Federkennlinie aufweisen.At the in FIG. 1 shown embodiment of the pump unit 10, the pump unit 10 on a balance piston 40. The balance piston 40 is arranged in a balance piston channel 45. The compensation channel has a second axis A2 along which the compensating piston 40 is movably arranged in the compensation channel. The compensating piston 40 is likewise directly hydraulically coupled to the working space 20. Furthermore, the pump unit 10 comprises a spring element 50. The spring element 50 is mechanically coupled to the first end of the compensating piston 40 facing away from the working space 20. The spring element 50 is formed, depending on a force acting on the spring element 50, a position of the balance piston 40 to influence. The spring element 50 may in this case have, for example, a degressive spring characteristic.

Eine vorteilhafte Auslegung des Ausgleichskolbens 40 und des Federelements 50 bei einem Pumpkolben 30 mit einem Durchmesser von 10 mm und einem Hub von 2 mm ist:

  • Durchmesser des Ausgleichskolbens 40: 10 mm
  • Maximaler Hub des Ausgleichskolbens 40: 4,2 mm
  • Masse des Ausgleichskolbens 40: 8 g
  • Federelement 50: Federkonstante 20, 3 N/mm, Vorspannung 1900 N
An advantageous design of the balance piston 40 and the spring element 50 in a pump piston 30 with a diameter of 10 mm and a stroke of 2 mm is:
  • Diameter of balance piston 40: 10 mm
  • Maximum stroke of the balance piston 40: 4.2 mm
  • Mass of balance piston 40: 8 g
  • Spring element 50: spring constant 20, 3 N / mm, preload 1900 N

Der Ausgleichskolben 40 beginnt eine Bewegung erst dann, wenn der Druck in dem Arbeitsraum 20 einen vorgegebenen Wert überschreitet. Vorzugsweise ist dieser vorgegebene Druck in dem Arbeitsraum 20 ca. 245 bar. Der Ausgleichskolben 40 beendet seine Bewegung, sobald der Druck in dem Arbeitsraum 20 einen weiteren vorgegebenen Wert überschreitet. Vorzugsweise ist dieser weitere vorgegebene Druck in dem Arbeitsraum 20 ca. 258 bar. Damit kann erreicht werden, dass bei einem Druck in dem Arbeitsraum 20 von ca. 245 bar der Ausgleichskolben 40 die Volumenänderung in dem Arbeitsraum 20 durch den Pumpkolben 30 kompensiert, und so ein weiterer Druckanstieg in dem Arbeitsraum 20 vermieden werden kann. Damit kann der Druck in dem Arbeitsraum 20 mittels des Ausgleichskolbens 40 auf einen Wert von ca. 245 bar begrenzt werden. Dies ist insbesondere gezeigt in Figur 7 mit einer schematische Ansicht der funktionalen Abhängigkeit des Hubs des Ausgleichskolbens 40 der Pumpeneinheit 10 von dem Druck in dem Arbeitsraum 20.The balance piston 40 starts a movement only when the pressure in the working space 20 exceeds a predetermined value. Preferably, this predetermined pressure in the working space 20 is about 245 bar. The balance piston 40 stops its movement as soon as the pressure in the working space 20 exceeds another predetermined value. Preferably, this further predetermined pressure in the working space 20 is about 258 bar. It can thus be achieved that at a pressure in the working chamber 20 of about 245 bar, the compensating piston 40 compensates for the change in volume in the working space 20 by the pump piston 30, and so a further increase in pressure in the working space 20 can be avoided. Thus, the pressure in the working chamber 20 can be limited by means of the balancing piston 40 to a value of about 245 bar. This is especially shown in FIG. 7 with a schematic view of the functional dependence of the stroke of the balance piston 40 of the pump unit 10 of the pressure in the working space 20th

Darüber hinaus sind in den Figuren 8a, 8b und 8c die Druckverläufe am Austritt der Pumpeneinheit 10 (Figur 8a) und im Kraftstoffspeicher 220 (Figur 8b) sowie Injektoreinspritzmengen in Abhängigkeit von einer Drehzahl der Pumpeneinheit 10 (Figur 8c) dargestellt. So ist insbesondere in Figur 8a gezeigt, dass der Druck am Austritt der Pumpeneinheit 10 mittels des Ausgleichskolbens 40 insbesondere bei höheren Drehzahlen (hier ab ca. 4.800) auf einen Wert von ca. 245 bar begrenzt werden kann (siehe Grenze G zwischen dem dunklen und dem helleren Bereich).In addition, in the Figures 8a, 8b and 8c the pressure curves at the outlet of the pump unit 10 ( FIG. 8a ) and in the fuel tank 220 ( FIG. 8b ) as well as injector injection quantities as a function of a rotational speed of the pump unit 10 (FIG. FIG. 8c ). So is in particular in FIG. 8a shown that the pressure at the outlet of the pump unit 10 by means of the balance piston 40, in particular at higher speeds (here from about 4,800) can be limited to a value of about 245 bar (see boundary G between the dark and the lighter area).

Der Ausgleichskolben 40 kann beispielsweise derart in dem Pumpengehäuse 15 angeordnet sein, dass die Längsachse L1 des Pumpkolbenkanals 36 und die zweite Achse A2 einen vorgegebenen Winkel einschließen. Insbesondere kann der Ausgleichskolbenkanal 45 gegenüber dem Pumpkolbenkanal 36 ebenfalls entlang der Längsachse L1 angeordnet sein.The compensating piston 40 may for example be arranged in the pump housing 15 such that the longitudinal axis L1 of the pump piston channel 36 and the second axis A2 include a predetermined angle. In particular, the compensating piston channel 45 can also be arranged opposite the pump piston channel 36 along the longitudinal axis L1.

Das Federelement 50 kann beispielsweise in einem weiteren Gefäß 60 der Pumpeneinheit 10 angeordnet sein. In dem Gefäß 60 kann das Federelement 50 derart angeordnet sein, dass das Federelement 50 eine Vorspannung aufweist.The spring element 50 can be arranged, for example, in a further vessel 60 of the pump unit 10. In the vessel 60, the spring element 50 may be arranged such that the spring element 50 has a bias voltage.

Figur 2 zeigt ein zweites Ausführungsbeispiel der Pumpeneinheit 10, bei dem das Federelement 50 in einem Druckausgleichsgefäß 60' angeordnet ist. Das Federelement 50 kann hierbei zusätzlich genutzt werden, Druckpulsationen zu dämpfen. Hierzu ist in dem in Figur 2 gezeigten Ausführungsbeispiel zwischen dem Ausgleichskolben 40 und dem Federelement 50 ein bewegliches Element 70, beispielsweise eine Rollmembran, eingespannt. FIG. 2 shows a second embodiment of the pump unit 10, in which the spring element 50 is arranged in a pressure equalization vessel 60 '. The spring element 50 can additionally be used to dampen pressure pulsations. This is in the in FIG. 2 shown embodiment between the balance piston 40 and the spring element 50, a movable member 70, for example, a rolling diaphragm, clamped.

Figur 3 zeigt ein drittes Ausführungsbeispiel der Pumpeneinheit 10, bei der die Pumpeneinheit 10 eine kombinierte Anordnung des Ausgleichskolbens 40 und dem Einlassventil aufweist. Beispielsweise kann der Ausgleichskolben 40 das Einlassventil umfassen. FIG. 3 shows a third embodiment of the pump unit 10, wherein the pump unit 10 has a combined arrangement of the balance piston 40 and the inlet valve. For example, the balance piston 40 may include the inlet valve.

Figur 4 zeigt ein viertes Ausführungsbeispiel der Pumpeneinheit 10. Im Unterschied zu dem in Figur 1 gezeigten Ausführungsbeispiel weist die Pumpeneinheit 10 einen ersten Pumpkolben 32 und einen zweiten Pumpkolben 34 auf. Der erste Pumpkolben 32 ist in dem Pumpkolbenkanal 36 entlang der Längsachse L1 beweglich angeordnet und direkt hydraulisch gekoppelt mit dem Arbeitsraum 20. Der zweite Pumpkolben 34 ist ebenfalls in dem Pumpkolbenkanal 36 entlang der Längsachse L1 beweglich angeordnet und ist über das Federelement 50 gekoppelt mit dem ersten Pumpkolben 32, wobei das Federelement 50 ausgebildet ist, abhängig von einem Druck in dem Arbeitsraum 20 einen Abstand zwischen dem ersten 32 und dem zweiten Pumpkolben 34 anzupassen. Das Federelement 50 ist ausgebildet, bei einem Förderhub des zweiten Pumpkolbens 34 bis zum Erreichen eines vorgegebenen Drucks in dem Arbeitsraum 20 den Abstand zwischen dem ersten 32 und zweiten Pumpkolben 34 im Wesentlichen unverändert zu lassen und im Sinne eines Konstanthaltens des Drucks in dem Arbeitsraum 20 im Verlauf einer Fortsetzung des Förderhubs des zweiten Pumpkolbens 34 den Abstand anzupassen. Der erste Pumpkolben 32 weist an einem dem zweiten Pumpkolben 34 zugewandten ersten Ende eine Ausnehmung 90 auf. In der Ausnehmung 90 ist das Federelement 50 angeordnet. Alternativ kann das Federelement außerhalb des ersten Pumpkolbens angeordnet sein. Der zweite Pumpkolben 34 weist an einem dem ersten Pumpkolben 32 zugewandten ersten Ende einen Stößel 80 auf. Der Stößel 80 ist mechanisch gekoppelt mit dem Federelement 50. FIG. 4 shows a fourth embodiment of the pump unit 10. In contrast to the in FIG. 1 In the embodiment shown, the pump unit 10 has a first pump piston 32 and a second pump piston 34. The first pump piston 32 is movably arranged in the pump piston channel 36 along the longitudinal axis L1 and directly hydraulically coupled to the working space 20. The second pump piston 34 is also movably arranged in the pump piston channel 36 along the longitudinal axis L1 and is coupled via the spring element 50 with the first Pumping piston 32, wherein the spring element 50 is formed, depending on a pressure in the working space 20 to adjust a distance between the first 32 and the second pump piston 34. The spring element 50 is designed to leave the distance between the first 32 and second pump piston 34 substantially unchanged during a delivery stroke of the second pump piston 34 until a predetermined pressure in the working space 20 is reached, and to keep the pressure in the working space 20 constant in the process Course of a continuation of the delivery stroke of the second pump piston 34 to adjust the distance. The first pumping piston 32 has a recess 90 at a first end facing the second pumping piston 34. In the recess 90, the spring element 50 is arranged. Alternatively, the spring element may be arranged outside of the first pump piston. The second pump piston 34 has a plunger 80 at a first end facing the first pump piston 32. The plunger 80 is mechanically coupled to the spring element 50.

Figur 5 zeigt ein fünftes Ausführungsbeispiel der Pumpeneinheit 10. Im Unterschied zu dem in Figur 4 gezeigten Ausführungsbeispiel ist der zweite Pumpkolben 34 über ein Ausgleichsvolumen 100 hydraulisch gekoppelt mit dem ersten Pumpkolben 32, wobei das Ausgleichsvolumen 100 hydraulisch gekoppelt ist mit einer Ausgleichseinheit 110, die ausgebildet ist, abhängig von einem Druck in dem Arbeitsraum 20 das Ausgleichsvolumen 100 anzupassen. Die Ausgleichseinheit 110 ist beispielsweise ausgebildet, bei einem Förderhub des Pumpkolbens bis zum Erreichen eines vorgegebenen Drucks in dem Arbeitsraum 20 das Ausgleichsvolumen 100 im Wesentlichen unverändert zu lassen und im Sinne eines Konstanthaltens des Drucks in dem Arbeitsraum 20 im Verlauf einer Fortsetzung des Förderhubs das Ausgleichsvolumen 100 anzupassen. FIG. 5 shows a fifth embodiment of the pump unit 10. In contrast to the in FIG. 4 In the exemplary embodiment shown, the second pump piston 34 is hydraulically coupled to the first pump piston 32 via a compensation volume 100, wherein the compensation volume 100 is hydraulically coupled to a compensation unit 110, which is designed to adjust the compensation volume 100 depending on a pressure in the working space 20. The compensation unit 110 is formed, for example, at a delivery stroke of the pump piston until reaching a predetermined pressure in the working chamber 20 to leave the compensation volume 100 substantially unchanged and in the sense of keeping the pressure in the working chamber 20 constant in the course of a continuation of the delivery stroke, the compensation volume 100.

Die Ausgleichseinheit 110 umfasst beispielsweise eine Ausgleichskammer 120, die in dem Pumpengehäuse 15 angeordnet ist. Vorzugsweise weist die Ausgleichskammer eine Öffnung auf, über die die Ausgleichskammer widerstandsfrei hydraulisch gekoppelt ist mit einem Pumpenzulauf Des Weiteren umfasst die Ausgleichseinheit 110 ein weiteres Federelement 50', das in der Ausgleichskammer 120 angeordnet ist. Die Ausgleichseinheit 110 umfasst des Weiteren einen Kolben 130, der in der Ausgleichskammer 120 entlang einer dritten Achse beweglich angeordnet ist. Der Kolben ist an einem ersten Ende mechanisch gekoppelt mit dem weiteren Federelement 50' und an einem zweiten Ende direkt hydraulisch gekoppelt mit dem Arbeitsvolumen. Das weitere Federelement 50' kann eine Federkennlinie mit einem degressiven Verlauf aufweisen. Ferner kann das weitere Federelement 50' derart angeordnet und ausgebildet sein, dass es eine vorgegebene Vorspannung aufweist.The compensation unit 110 includes, for example, a compensation chamber 120, which is arranged in the pump housing 15. Preferably, the compensation chamber has an opening, via which the compensation chamber is hydraulically coupled without resistance to a pump inlet. Furthermore, the compensation unit 110 comprises a further spring element 50 ', which is arranged in the compensation chamber 120. The compensation unit 110 further comprises a piston 130, which is arranged movably in the compensation chamber 120 along a third axis. The piston is mechanically coupled at a first end to the further spring element 50 'and at a second end directly hydraulically coupled to the working volume. The further spring element 50 'may have a spring characteristic with a degressive course. Further, the further spring element 50 'may be arranged and configured such that it has a predetermined bias voltage.

Claims (4)

Pumpeneinheit (10) für eine Hochdruckpumpe, umfassend: - ein Pumpengehäuse (15), das einen Niederdruckeingang (17) aufweist, über den einem im dem Pumpengehäuse (15) ausgebildeten Arbeitsraum (20) ein Arbeitsmedium zugeführt wird, und einen Hochdruckausgang (19), über den das Arbeitsmedium aus dem Arbeitsraum (20) abgeleitet wird, - einen in dem Pumpengehäuse (15) ausgebildeter Pumpkolbenkanal (36) mit einer Längsachse (L1), - einen Pumpenkolben, der entlang der Längsachse (L1) beweglich in dem Pumpkolbenkanal (36) angeordnet ist und der direkt hydraulisch mit dem Arbeitsraum (20) gekoppelt ist, - einen Ausgleichskolben (40), der direkt hydraulisch mit dem Arbeitsraum (20) gekoppelt ist und der in einem Ausgleichskolbenkanal (45) mit einer weiteren Achse (A3) beweglich angeordnet ist, und - ein Federelement (50), das an einem dem Arbeitsraum (20) abgewandten Ende des Ausgleichskolbens (40) mit diesem mechanisch gekoppelt ist und ausgebildet ist, abhängig von einer Kraft, die auf das Federelement (50) wirkt, eine Position des Ausgleichskolbens (40) zu beeinflussen, wobei der Ausgleichskolben (40) ein Einlassventil umfasst. Pump unit (10) for a high-pressure pump, comprising: - A pump housing (15) having a low pressure input (17), via which in the pump housing (15) formed in a working space (20), a working medium is supplied, and a high-pressure outlet (19) through which the working fluid from the working space (20 ) is derived, a pump piston channel (36) formed in the pump housing (15) with a longitudinal axis (L1), a pump piston which is arranged movably in the pump piston channel along the longitudinal axis and which is directly hydraulically coupled to the working space, - A compensating piston (40) which is directly hydraulically coupled to the working space (20) and which is arranged in a compensating piston channel (45) with a further axis (A3) movable, and a spring element (50) which is mechanically coupled to an end of the compensating piston (40) facing away from the working space (20) and is designed, depending on a force acting on the spring element (50), a position of the compensating piston ( 40), wherein the compensating piston (40) comprises an inlet valve. Pumpeneinheit (10) nach Anspruch 1, bei der ein Druck in dem Arbeitsraum (20) mittels des Ausgleichskolbens (40) auf einen Wert von maximal ca. 250 bar begrenzt ist.Pump unit (10) according to claim 1, wherein a pressure in the working space (20) by means of the compensating piston (40) is limited to a maximum value of about 250 bar. Pumpeneinheit (10) nach einem der vorstehenden Ansprüche, bei der das Federelement (50) eine Federkennlinie mit einem degressiven Verlauf aufweist.Pump unit (10) according to one of the preceding claims, wherein the spring element (50) has a spring characteristic with a degressive course. Pumpeneinheit (10) nach einem der vorstehenden Ansprüche bei der das Federelement (50) eine vorgegebene Vorspannung aufweist.Pump unit (10) according to one of the preceding claims wherein the spring element (50) has a predetermined bias.
EP16157416.5A 2011-01-31 2012-01-30 Pump unit for a high-pressure pump Not-in-force EP3059439B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011003396A DE102011003396A1 (en) 2011-01-31 2011-01-31 Pump unit for a high-pressure pump
EP12702790.2A EP2670971B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP12702790.2A Division EP2670971B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump
EP12702790.2A Division-Into EP2670971B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump

Publications (2)

Publication Number Publication Date
EP3059439A1 true EP3059439A1 (en) 2016-08-24
EP3059439B1 EP3059439B1 (en) 2018-06-13

Family

ID=45566987

Family Applications (4)

Application Number Title Priority Date Filing Date
EP16157404.1A Not-in-force EP3059437B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump
EP16157416.5A Not-in-force EP3059439B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump
EP16157410.8A Not-in-force EP3059438B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump
EP12702790.2A Not-in-force EP2670971B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP16157404.1A Not-in-force EP3059437B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP16157410.8A Not-in-force EP3059438B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump
EP12702790.2A Not-in-force EP2670971B1 (en) 2011-01-31 2012-01-30 Pump unit for a high-pressure pump

Country Status (6)

Country Link
US (1) US10047740B2 (en)
EP (4) EP3059437B1 (en)
CN (1) CN103443440B (en)
BR (1) BR112013019539A2 (en)
DE (1) DE102011003396A1 (en)
WO (1) WO2012104236A2 (en)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9422898B2 (en) * 2013-02-12 2016-08-23 Ford Global Technologies, Llc Direct injection fuel pump
DE102014209288A1 (en) * 2014-05-16 2015-11-19 Robert Bosch Gmbh Piston pump, in particular fuel pump for a fuel system for an internal combustion engine
WO2018091306A1 (en) * 2016-11-15 2018-05-24 Mhwirth Gmbh Method for operating a piston pump, and piston pump
JP6919314B2 (en) * 2017-05-11 2021-08-18 株式会社デンソー Pulsation damper and fuel pump device
CN110195673B (en) * 2018-02-27 2021-05-14 纬湃汽车电子(长春)有限公司 High pressure pump
CN109209710A (en) * 2018-11-14 2019-01-15 上海华羿汽车系统集成有限公司 A kind of plunger fuel injector and internal combustion engine
CN109209713B (en) * 2018-11-14 2024-03-19 上海华羿汽车系统集成有限公司 Plunger device and internal combustion engine
CN109695566A (en) * 2019-01-18 2019-04-30 郑国璋 A kind of sealing lubrication structure of plunger pump
CN110630461B (en) * 2019-09-24 2021-02-05 浙江瑞程石化技术有限公司 Variable radial plunger pump
GB2600765B (en) * 2020-11-10 2023-04-05 Delphi Tech Ip Ltd Fuel pump assembly
US11939941B2 (en) 2022-03-24 2024-03-26 Delphi Technologies Ip Limited Gasoline direct injection fuel pump with isolated plunger sleeve

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB369541A (en) * 1929-11-23 1932-03-24 Bosch Robert Improvements in and relating to the controlling of fuel injection pumps of internal combustion engines
CH158033A (en) * 1931-08-17 1932-10-31 Sulzer Ag Fuel pump for injection internal combustion engines with an accumulator piston in the pump cylinder.
US4881504A (en) * 1987-02-13 1989-11-21 Lucas Industries Public Limited Company Fuel injection pump
EP1403509A2 (en) * 2002-09-27 2004-03-31 Robert Bosch Gmbh Pressure limiting device and fuel system with such a pressure limiting device

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1154798A (en) * 1912-07-29 1915-09-28 Charles Otis Palmer Governor for air-compressors.
US1610997A (en) * 1923-05-11 1926-12-14 Cafferata Domenico L Hendrikus Fuel pump for internal-combustion engines
US2011165A (en) * 1931-08-17 1935-08-13 Firm Sulzer Freres Sa Winterth Fuel injection pump for internal combustion engines
US2011166A (en) * 1931-08-18 1935-08-13 Sulzer Ag Fuel injection pump for internal combustion engines
US2019650A (en) * 1931-11-16 1935-11-05 Bischof Bernhard Fuel injection apparatus for internal combustion engines
US1968961A (en) * 1931-11-25 1934-08-07 Schaeren Ernst Fuel injection device for internal combustion engines
US2071237A (en) * 1934-08-16 1937-02-16 Rupprecht Tom Fuel injector for diesel engines
US2720842A (en) * 1949-06-07 1955-10-18 Lucas Ltd Joseph Pumps
US3003421A (en) * 1956-08-14 1961-10-10 Bessiere Pierre Etienne Reciprocating liquid pumps, and in particular in fuel injection pumps
JPS4912401A (en) * 1972-05-17 1974-02-02
US4394962A (en) 1981-02-23 1983-07-26 Cummins Engine Company, Inc. Solenoid operated fuel injector and control valve
JPS58149566U (en) 1982-03-31 1983-10-07 株式会社デンソー distribution type fuel injection pump
IT1221912B (en) * 1987-12-09 1990-07-12 Weber Srl VARIABLE DISPLACEMENT FUEL INJECTION PUMP FOR DIESEL ENGINE INJECTION EQUIPMENT
DE3912106C2 (en) * 1988-05-02 1996-05-02 Volkswagen Ag Fuel injector
US5107890A (en) * 1990-05-03 1992-04-28 Huron Products Industries, Inc. Ball check valve
DE4217940A1 (en) 1992-05-30 1993-12-02 Bosch Gmbh Robert Fuel injection pump for internal combustion engines
US5785505A (en) * 1996-10-21 1998-07-28 Caterpillar Inc. Integral fluid pump and internal combustion engine
DE19644915A1 (en) * 1996-10-29 1998-04-30 Bosch Gmbh Robert high pressure pump
DE19834120A1 (en) * 1998-07-29 2000-02-03 Bosch Gmbh Robert Fuel supply system of an internal combustion engine
GB9918871D0 (en) 1999-08-10 1999-10-13 Lucas Ind Plc Fuel pump
JP2001123913A (en) 1999-10-27 2001-05-08 Toyota Motor Corp Fuel injection device for internal combustion engine
DE10355027A1 (en) 2003-11-25 2005-06-23 Robert Bosch Gmbh High-pressure pump, in particular for a fuel injection device of an internal combustion engine
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
US20070189911A1 (en) * 2006-02-16 2007-08-16 Campbell Hausfeld/Scott Fetzer Company Liquid pump

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB369541A (en) * 1929-11-23 1932-03-24 Bosch Robert Improvements in and relating to the controlling of fuel injection pumps of internal combustion engines
CH158033A (en) * 1931-08-17 1932-10-31 Sulzer Ag Fuel pump for injection internal combustion engines with an accumulator piston in the pump cylinder.
US4881504A (en) * 1987-02-13 1989-11-21 Lucas Industries Public Limited Company Fuel injection pump
EP1403509A2 (en) * 2002-09-27 2004-03-31 Robert Bosch Gmbh Pressure limiting device and fuel system with such a pressure limiting device

Also Published As

Publication number Publication date
EP3059438A1 (en) 2016-08-24
EP3059439B1 (en) 2018-06-13
US10047740B2 (en) 2018-08-14
EP3059438B1 (en) 2018-03-14
CN103443440B (en) 2016-02-24
BR112013019539A2 (en) 2016-10-04
EP2670971B1 (en) 2017-03-15
WO2012104236A3 (en) 2012-11-01
CN103443440A (en) 2013-12-11
EP3059437A1 (en) 2016-08-24
EP2670971A2 (en) 2013-12-11
US20140050597A1 (en) 2014-02-20
DE102011003396A1 (en) 2012-08-02
WO2012104236A2 (en) 2012-08-09
EP3059437B1 (en) 2018-06-06

Similar Documents

Publication Publication Date Title
EP2670971B1 (en) Pump unit for a high-pressure pump
DE102004013307B4 (en) High-pressure fuel pump with a pressure relief valve
EP1411238B1 (en) Pressure regulating valve for an injection system
EP1352174B1 (en) Fuel-injection system comprising pressure regulation in the return line
DE10327411B4 (en) Pressure relief valve and fuel system with such a pressure relief valve
EP2467591B1 (en) Fuel delivery device for a fuel injection device of an internal combustion engine
DE102008059117B4 (en) High-pressure pump assembly
WO2003067072A9 (en) Fuel injection device for a combustion engine
DE102008043217A1 (en) High-pressure fuel pump for an internal combustion engine
EP1218631B1 (en) Pressure amplifier and a fuel injection system with a pressure amplifier
EP1357283B1 (en) Fuel injection system for internal combustion engine
DE10139055A1 (en) Method, computer program, control and / or regulating device and fuel system for an internal combustion engine
WO2013075946A1 (en) Fuel delivery system for a vehicle
WO2004027250A1 (en) Fuel injection unit for internal combustion engines
DE19839579C1 (en) Two=stage filtering system for fuel supply to injectors
WO2012089376A1 (en) Pump, in particular a fuel injection system
EP2659127B1 (en) Pressure switching valve for a fuel injection system of an internal combustion engine
DE102007037084A1 (en) Fuel high pressure pump for fuel injection system of internal combustion engine, has pumping element with element space that is connected with low pressure, where quantity or pressure compensating device is attached to suction valve
DE10210300B4 (en) Pump element for a high-pressure pump and high-pressure pump with controllable flow rate
EP1655480A1 (en) Method of using a fuel system of an internal combustion engine and fuel system
EP1515038B1 (en) Fuel system for an internal combustion engine
DE102009057927B4 (en) Pump and method for conveying a fluid
DE102009047113A1 (en) Fuel supply device has supply pump, high pressure pump and flow limiting throttle in supply line for supply pump, where flow limiting throttle is mechanically coupled with overflow valve
DE102004007317A1 (en) High-pressure fuel pump for an internal combustion engine has non-return valves and pressure-control valves between a feed chamber and a common rail
DE102010041487A1 (en) Fuel injection system

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: 2670971

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20170224

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20170410

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20180109

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

AC Divisional application: reference to earlier application

Ref document number: 2670971

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 1008767

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180615

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502012012900

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20180613

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180913

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180913

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

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180914

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

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

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

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

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181013

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502012012900

Country of ref document: DE

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

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

Ref country code: FR

Payment date: 20190124

Year of fee payment: 8

Ref country code: GB

Payment date: 20190121

Year of fee payment: 8

26N No opposition filed

Effective date: 20190314

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

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502012012900

Country of ref document: DE

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: LU

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

Effective date: 20190130

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20190131

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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: 20190801

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

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

Ref country code: BE

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

Effective date: 20190131

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

Ref country code: CH

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

Effective date: 20190131

Ref country code: LI

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

Effective date: 20190131

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

Ref country code: IE

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

Effective date: 20190130

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 1008767

Country of ref document: AT

Kind code of ref document: T

Effective date: 20190130

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

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

Ref country code: AT

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

Effective date: 20190130

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502012012900

Country of ref document: DE

Owner name: VITESCO TECHNOLOGIES GMBH, DE

Free format text: FORMER OWNER: CONTINENTAL AUTOMOTIVE GMBH, 30165 HANNOVER, DE

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20181015

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613

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

Effective date: 20200130

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

Ref country code: FR

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

Effective date: 20200131

Ref country code: GB

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

Effective date: 20200130

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

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20120130

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

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20180613