EP2670971B1 - Unité pompe pour une pompe haute pression - Google Patents

Unité pompe pour une pompe haute pression Download PDF

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Publication number
EP2670971B1
EP2670971B1 EP12702790.2A EP12702790A EP2670971B1 EP 2670971 B1 EP2670971 B1 EP 2670971B1 EP 12702790 A EP12702790 A EP 12702790A EP 2670971 B1 EP2670971 B1 EP 2670971B1
Authority
EP
European Patent Office
Prior art keywords
pump
piston
pressure
working space
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.)
Not-in-force
Application number
EP12702790.2A
Other languages
German (de)
English (en)
Other versions
EP2670971A2 (fr
Inventor
Michael Absmeier
Xaver GEBHARDT
Anatoliy Lyubar
Danica Stegemann
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
Priority to EP16157404.1A priority Critical patent/EP3059437B1/fr
Priority to EP16157416.5A priority patent/EP3059439B1/fr
Priority to EP16157410.8A priority patent/EP3059438B1/fr
Publication of EP2670971A2 publication Critical patent/EP2670971A2/fr
Application granted granted Critical
Publication of EP2670971B1 publication Critical patent/EP2670971B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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.
  • CH 158 033 A and US 4,449,504 A each describe a fuel pump for fuel injection engines, in which a pump piston and a pump piston opposite the accumulator piston are coupled directly hydraulically to a working space, the accumulator piston is spring loaded and so can cushion pressure fluctuations in the working space.
  • 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 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. 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 assembly.
  • 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 pump unit comprises 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.
  • 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 pump pistons essentially unchanged during a delivery stroke of the second pump piston until a predetermined pressure in the working space has been reached, and in the sense of a Keeping constant the pressure in the working space in the course of a continuation of the delivery stroke to adjust the distance.
  • the spring element causes that in the delivery stroke of the second pump piston on reaching the desired pressure in the working space of the first pump piston substantially comes to a standstill 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 operates in substantially the same way as a one-part pump piston known from the prior art.
  • the pressure in the working space by means of the second pump piston is limited to a maximum value of approximately 250 bar.
  • the pump unit comprises 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.
  • 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 via a compensation volume to the first pump piston, wherein the compensation volume is hydraulically coupled to a compensation unit, which is designed to adjust the compensation volume depending on a pressure in the working space.
  • the invention has the advantage that a separate between a fuel tank and the pump unit electromagnetic flow control valve is not required and / or adjusting the flow rate, for example, a current fuel consumption of the internal combustion engine by throttling an inlet flow and / or by Abreten an unneeded, compressed fuel quantity not is 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 that operates in substantially the same way as a one-piece pump piston known from the prior art.
  • the pump unit comprises 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. 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.
  • 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, depending on a force acting on the spring element.
  • the balance piston comprises an inlet valve.
  • 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 prefeed 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 example 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 supply 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 outlet valve prevents backflow of the working medium, for example from a rail, into the pump unit 10.
  • 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 has a balancing 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 balance 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 designed to influence a position of the compensation piston 40 as a function of a force acting on the spring element 50.
  • 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 approximately 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 approximately 258 bar. It can thus be achieved that at a pressure in the working space 20 of approximately 245 bar, the compensating piston 40 compensates for the change in volume in the working space 20 by the pump piston 30, and thus 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 compensating piston 40 to a value of about 245 bar. This is especially shown in FIG.
  • FIG. 8a the pressure curves at the outlet of the pump unit 10 ( FIG. 8a ) and in the fuel storage 220 ( FIG. 8b ) as well as injector injection quantities as a function of a rotational speed of the pump unit 10 (FIG. FIG. 8c ).
  • FIG. 8a 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 example 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 an inventive 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 includes the inlet valve
  • FIG. 4 shows an embodiment of the pump unit 10 not belonging to the invention.
  • 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 pump piston 32 has at a second pump piston 34 facing first End of a recess 90. 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 an example 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 designed, for example, to leave the compensation volume 100 essentially unchanged during a delivery stroke of the pump piston until a predetermined pressure in the working space 20 is reached and in order to keep the pressure in the working space 20 constant in the course of a continuation of the delivery stroke, the compensation volume 100 adapt.
  • 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 to a second end directly hydraulically coupled with 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)

  1. Unité de pompe (10) pour une pompe haute pression, comprenant :
    - un carter de pompe (15) qui présente une entrée basse pression (17) par le biais de laquelle un fluide de travail est acheminé à un espace de travail (20) réalisé dans le carter de pompe (15), et une sortie haute pression (19) par le biais de laquelle le fluide de travail est évacué hors de l'espace de travail (20),
    - un canal de piston de pompe (36) réalisé dans le carter de pompe (15) avec un axe longitudinal (Ll),
    - un piston de pompe qui est disposé de manière déplaçable le long de l'axe longitudinal (Ll) dans le canal de pompe de piston (36) et qui est accouplé hydrauliquement directement à l'espace de travail (20),
    - un piston d'équilibrage (40) qui est accouplé hydrauliquement directement à l'espace de travail (20) et qui est disposé de manière déplaçable dans un canal de piston d'équilibrage (45) avec un deuxième axe (A2), le canal de piston d'équilibrage (45) étant disposé par rapport au canal de piston de pompe (36) le long de l'axe longitudinal (Ll), et
    - un élément de ressort (50) qui est accouplé mécaniquement au niveau d'une extrémité du piston d'équilibrage (40) opposée à l'espace de travail (20) audit piston d'équilibrage et qui est réalisé de manière à influencer une position du piston d'équilibrage (40) en fonction d'une force qui agit sur l'élément de ressort (50),
    caractérisée en ce que le piston d'équilibrage (40) comprend une soupape d'entrée.
  2. Unité de pompe (10) selon la revendication 1, dans laquelle une pression dans l'espace de travail (20) est limitée au moyen du piston d'équilibrage (40) à une valeur maximale d'environ 250 bars.
  3. Unité de pompe (10) selon l'une quelconque des revendications précédentes, dans laquelle l'élément de ressort (50) présente une caractéristique de ressort avec une allure dégressive.
  4. Unité de pompe (10) selon l'une quelconque des revendications précédentes, dans laquelle l'élément de ressort (50) présente une précontrainte prédéfinie.
EP12702790.2A 2011-01-31 2012-01-30 Unité pompe pour une pompe haute pression Not-in-force EP2670971B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP16157404.1A EP3059437B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157416.5A EP3059439B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157410.8A EP3059438B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011003396A DE102011003396A1 (de) 2011-01-31 2011-01-31 Pumpeneinheit für eine Hochdruckpumpe
PCT/EP2012/051409 WO2012104236A2 (fr) 2011-01-31 2012-01-30 Unité pompe pour une pompe haute pression

Related Child Applications (6)

Application Number Title Priority Date Filing Date
EP16157410.8A Division-Into EP3059438B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157410.8A Division EP3059438B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157416.5A Division EP3059439B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157416.5A Division-Into EP3059439B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157404.1A Division-Into EP3059437B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157404.1A Division EP3059437B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression

Publications (2)

Publication Number Publication Date
EP2670971A2 EP2670971A2 (fr) 2013-12-11
EP2670971B1 true EP2670971B1 (fr) 2017-03-15

Family

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Family Applications (4)

Application Number Title Priority Date Filing Date
EP16157416.5A Not-in-force EP3059439B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157410.8A Not-in-force EP3059438B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP12702790.2A Not-in-force EP2670971B1 (fr) 2011-01-31 2012-01-30 Unité pompe pour une pompe haute pression
EP16157404.1A Not-in-force EP3059437B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP16157416.5A Not-in-force EP3059439B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression
EP16157410.8A Not-in-force EP3059438B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP16157404.1A Not-in-force EP3059437B1 (fr) 2011-01-31 2012-01-30 Unite de pompe pour une pompe a haute pression

Country Status (6)

Country Link
US (1) US10047740B2 (fr)
EP (4) EP3059439B1 (fr)
CN (1) CN103443440B (fr)
BR (1) BR112013019539A2 (fr)
DE (1) DE102011003396A1 (fr)
WO (1) WO2012104236A2 (fr)

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US9422898B2 (en) * 2013-02-12 2016-08-23 Ford Global Technologies, Llc Direct injection fuel pump
DE102014209288A1 (de) * 2014-05-16 2015-11-19 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoffpumpe für ein Kraftstoffsystem für eine Brennkraftmaschine
WO2018091306A1 (fr) * 2016-11-15 2018-05-24 Mhwirth Gmbh Procédé permettant de faire fonctionner une pompe à piston et pompe à piston
JP6919314B2 (ja) * 2017-05-11 2021-08-18 株式会社デンソー パルセーションダンパおよび燃料ポンプ装置
CN110195673B (zh) * 2018-02-27 2021-05-14 纬湃汽车电子(长春)有限公司 高压泵
CN109209713B (zh) * 2018-11-14 2024-03-19 上海华羿汽车系统集成有限公司 一种柱塞装置及内燃机
CN109209710A (zh) * 2018-11-14 2019-01-15 上海华羿汽车系统集成有限公司 一种柱塞喷油器及内燃机
CN109695566A (zh) * 2019-01-18 2019-04-30 郑国璋 一种柱塞泵的密封润滑结构
CN110630461B (zh) * 2019-09-24 2021-02-05 浙江瑞程石化技术有限公司 一种变量径向柱塞泵
US11939941B2 (en) 2022-03-24 2024-03-26 Delphi Technologies Ip Limited Gasoline direct injection fuel pump with isolated plunger sleeve

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US4449504A (en) * 1982-03-31 1984-05-22 Nippondenso Co., Ltd. Distributor type fuel injection pump
US4881504A (en) * 1987-02-13 1989-11-21 Lucas Industries Public Limited Company Fuel injection pump
EP1403509A2 (fr) * 2002-09-27 2004-03-31 Robert Bosch Gmbh Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression

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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
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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 (de) * 1931-08-17 1932-10-31 Sulzer Ag Brennstoffpumpe für Einspritz-Brennkraftmaschinen mit einem Speicherkolben im Pumpenzylinder.
US4449504A (en) * 1982-03-31 1984-05-22 Nippondenso Co., Ltd. Distributor type fuel injection pump
US4881504A (en) * 1987-02-13 1989-11-21 Lucas Industries Public Limited Company Fuel injection pump
EP1403509A2 (fr) * 2002-09-27 2004-03-31 Robert Bosch Gmbh Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression

Also Published As

Publication number Publication date
EP3059439B1 (fr) 2018-06-13
EP3059438A1 (fr) 2016-08-24
BR112013019539A2 (pt) 2016-10-04
EP3059438B1 (fr) 2018-03-14
US20140050597A1 (en) 2014-02-20
WO2012104236A3 (fr) 2012-11-01
EP3059437B1 (fr) 2018-06-06
WO2012104236A2 (fr) 2012-08-09
CN103443440B (zh) 2016-02-24
EP3059437A1 (fr) 2016-08-24
EP3059439A1 (fr) 2016-08-24
EP2670971A2 (fr) 2013-12-11
DE102011003396A1 (de) 2012-08-02
CN103443440A (zh) 2013-12-11
US10047740B2 (en) 2018-08-14

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