EP2278150B1 - Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne - Google Patents

Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne Download PDF

Info

Publication number
EP2278150B1
EP2278150B1 EP10180722A EP10180722A EP2278150B1 EP 2278150 B1 EP2278150 B1 EP 2278150B1 EP 10180722 A EP10180722 A EP 10180722A EP 10180722 A EP10180722 A EP 10180722A EP 2278150 B1 EP2278150 B1 EP 2278150B1
Authority
EP
European Patent Office
Prior art keywords
pressure
gas volume
diaphragms
membrane
housing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP10180722A
Other languages
German (de)
English (en)
Other versions
EP2278150A1 (fr
Inventor
Klaus Lang
Helmut Rembold
Wolfgang Bueser
Weidong Qi
Marcus Wuenning
Albrecht Baessler
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority claimed from EP03015623A external-priority patent/EP1411236B1/fr
Publication of EP2278150A1 publication Critical patent/EP2278150A1/fr
Application granted granted Critical
Publication of EP2278150B1 publication Critical patent/EP2278150B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0041Means for damping pressure pulsations
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M55/00Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/54Arrangement of fuel pressure regulators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0033Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical spring
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00Pumping installations or systems
    • F04B23/04Combinations of two or more pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047Layout or arrangement of systems for feeding fuel
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/02Fuel-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
    • F02M63/0225Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a device for damping pressure pulsations in a fluid system, in particular in a fuel system of an internal combustion engine, with a housing and with at least one working space, which communicates at least partially with the fluid system.
  • Such a device is from the DE 195 39 885 A1 known.
  • a fuel system of an internal combustion engine with direct fuel injection From a prefeed pump, the fuel is conveyed to a high-pressure piston pump, which compresses the fuel to a very high pressure.
  • the fuel enters a fuel rail ("Rail").
  • the high-pressure piston pump is driven by a camshaft of the internal combustion engine.
  • a quantity control valve is provided in order to adjust the delivery rate of the high pressure piston pump independently of the speed of the camshaft.
  • the delivery chamber of the high-pressure piston pump can be connected during a delivery stroke for a short time with the region of the fuel system located between the electric prefeed pump and the high-pressure fuel pump.
  • a pressure damper is provided there. This consists of a housing and a piston which is biased by a spring.
  • a pressure damper which works with a spring-biased rubber membrane.
  • a stopper is present, against which the membrane is supported at low pressure.
  • the pressure between the prefeed pump and the high-pressure piston pump is approximately constant. However, in modern fuel systems, this pressure can be variable. Typically, it is between 0.5 and 8 bar, with an overload safety must be present to about 10 to 12 bar. If the known pressure damper, which has a rubber membrane used in such a fuel system, there is a risk that at At a low system pressure, for example, of 0.5 bar and the superimposed pressure pulsations, the rubber membrane abuts against the stop. As a result, the damping effect of the pressure damper is weakened and it can damage the rubber membrane occur. The from the DE 195 39 885 A1 known pressure damper with a piston and a spring in turn would have to build very large when used in such a variable-pressure fuel system.
  • the present invention therefore has the object, a device of the type mentioned in such a way that it can be used in a fuel system with variable form, but it builds small and has a long life.
  • the compressibility of gases can be exploited to ensure the elastic movement of the membrane required to dampen pressure pulsations.
  • the membrane is not affected by any mechanical elements, which significantly increases their service life and reduces the risk of damage.
  • such a gas volume can be realized in almost any geometric shape. So it can be very to save space in the fluid system.
  • Another advantage of the device according to the invention is that it can be dispensed with a leakage line, which simplifies the construction of the fuel system again.
  • a membrane made of metal has several advantages: First, such a membrane is very dense compared to conventional gases and also to fluids. In particular, the high density of metal membranes in comparison to HC emissions plays a positive role here. On the other hand occurs in a metal diaphragm even at low pressures, for example. With the engine OFF, no overstretching over time, so that a damper device can be used with a metal diaphragm in a fluid system, which has a variable fluid pressure in a wide range.
  • the membrane and / or the housing is magnetic.
  • appropriate manufacturing processes for example, mechanical rolling and embossing
  • Umformmartensit material martensitic structure
  • the device can trap existing magnetic dirt particles in the fluid and prevent their further distribution. This increases the reliability of the components present in the fluid system, for example a pump.
  • costs are saved, since the complex demagnetization of the component is eliminated. Since no directly abutting and relatively movable parts are present in the device, the trapped dirt particles cause no functional damage to the device.
  • the gas volume is formed by a thin-walled and at its ends gas-tight closed metal tube. This is very easy and inexpensive to realize.
  • At least one outer wall of the working space is likewise designed as a membrane, an additional hydraulically effective area is obtained in a minimum space.
  • the effectiveness of the device according to the invention is thereby significantly increased again, while requiring little space.
  • the enclosed gas volume has a defined pressure at a standard external pressure (for example 1013 hPa), preferably an overpressure.
  • a standard external pressure for example 1013 hPa
  • an overpressure With such a defined pressure, the "spring stiffness" can be adjusted.
  • an overpressure in the trapped gas volume in Vergleizh To Aubendschreib be ge noirlht, because thereby the entire possible voltage range (tension and pressure) of the membrane material can be exploited.
  • a negative pressure or standard pressure Preferably, such an internal overpressure is selected which corresponds to approximately half of the maximum operating overpressure, less the pressure increase which arises due to the compression of the component.
  • the membrane geometry can be designed for higher strokes and lower pressure load or small installation volume.
  • the gas volume may have a closable opening, via which the pressure can be adjusted. This facilitates the production of the gas volume. Otherwise, the production would have to be done even at a certain pressure.
  • the membrane has at least one bead.
  • the spring properties of the membrane itself and also their strength properties can be significantly influenced.
  • the membrane can thus optimally the individual requirements of the fluid system are adapted.
  • the damper with comparable volume can have even more damping volume, or alternatively be built smaller.
  • the beads may have different height and / or a different course and / or a different cross-section. In this way one can achieve an asymmetrical spring stiffness of the membrane depending on the load direction.
  • the beads can also be shaped so that the maximum stress does not occur at the edge of the membrane, and the mechanical stresses are distributed as evenly as possible over the surface of the membrane. Furthermore, the entire material bandwidth in the tensile and compressive stress range can be used by a corresponding membrane design.
  • the membrane has at least one stop area which comes into contact with a maximum deflection of the membrane with a counter surface.
  • the maximum deflection is chosen so that damage to the membrane, such as a plastic deformation, are just avoided.
  • the mating surface is formed on the housing, on a separate stop member, and / or on a further membrane.
  • the overload protection can therefore be realized in various very simple and inexpensive ways.
  • the stop surface on the housing can be made for example by deep drawing, which is very simple and inexpensive.
  • a separate stop member is inexpensive, with different stop members can be provided for a same damper, so that the same device can be easily adapted to different conditions of use.
  • the stop surface on another membrane in turn saves space.
  • the enclosed gas volume be reduced by a filling area.
  • This filling area can also be formed by the stop member (this then acts as a "filler") or a housing portion.
  • the spring stiffness of the device can be increased by reducing the gas volume.
  • the membrane may be thinner, resulting in good dynamics and small size.
  • an advantageous embodiment of the device according to the invention is that the gas volume is limited by at least two membranes which are clamped in the region of their edges. Such a pressure damper builds comparatively flat. All the more so, when the membranes are substantially parallel. It is basically of course conceivable that the gas volume is introduced into the space lying between the two membranes when they are joined, so that it is possible to dispense with a filling opening.
  • the edges of the two membrane are sealed together and clamped radially inwardly of the sealing line.
  • the connection is made by a weld, is prevented by this embodiment of the device according to the invention that the welds must withstand additional mechanical forces.
  • the sealing connection thus serves only for sealing and does not have to take on other tasks and can thus fulfill particularly high tightness requirements safely. For the evaluation of the durability of the pressure damper according to the invention so only the membranes themselves must be considered.
  • the clamping has a structural elasticity.
  • elasticity which is "constructively wanted”.
  • a retaining ring made of a rubber-elastic material may be used, or a metal support may be used which has a spring portion.
  • the clamping can attack at any location of the membrane, but particularly favorable is an approach in the region of a median plane of the two membranes.
  • the installation space of the device according to the invention is particularly small if the working space of the two membranes is subdivided into two fluid areas which communicate with one another by a fluid connection.
  • An annular spacer between the two membranes simply defines or increases the trapped volume of gas. In this case, it is inexpensive possible to form the fluid connection, which connects the two fluid areas of the working space with each other, in the spacer.
  • the device is integrated in a housing of a fuel pump.
  • the benefits of the invention are particularly noticeable, since such a fuel pump is usually to build very small.
  • Damping device can be accommodated in a particularly space-saving, if the working space comprises an annular space and the gas volume is also annular. It is particularly advantageous if the working space and the gas volume are arranged on a cylinder of a fuel pump at least approximately coaxially with the cylinder axis.
  • the pressure damper so to speak surrounds the cylinder and the existing in this piston, which additionally causes a noise attenuation.
  • the gas volume be arranged in the manner of a spiral in the annular space, wherein the spiral and the annular space are at least approximately coaxial.
  • a spiral results in a large deformation surface, which contributes to a particularly effective pulsation damping.
  • the effective area of the gas volume can be further increased if the spiral gas volume extends helically in the axial direction of the working space.
  • a further preferred embodiment of the device according to the invention is characterized in that the gas volume is filled with helium. This facilitates the detection of leakage.
  • the membrane is made of a strip material which has residual stresses. Such residual stresses lead during the forming process to a flat distortion, so that the material is discarded in the formed state.
  • This can now be used specifically for the simplification of the production of the membrane can, especially if it has at least one bellows section: Due to the delay namely a targeted separation of the non-pressurized state flat contiguous areas of the membrane is no longer required. The safe evacuation of the membrane and filling of the gas volume, for example with helium is therefore easy and reliable possible.
  • the order of assembly can be as follows: First, the individual sections ("segments") of the membrane are placed on top of each other and in a welding device "Stacked”. After closing the welding device whose interior is evacuated and filled with filling gas, such as helium, with a desired pressure. In this phase, the distorted membrane sections ensure that the filling gas flows safely into all cavities. Then the individual sections are pressed together and welded together.
  • filling gas such as helium
  • the membrane comprises at least one bead section and at least one bellows section. This allows the combination of the advantages of both versions.
  • the membrane has at its radially outer edge a fastening portion which extends approximately parallel to the central axis and is secured to the housing. In this way, the entire inner diameter of the housing can be used hydraulically effective, which minimizes the required space and reduces costs.
  • the device comprises a clamping device which acts on the mounting portion radially against the housing.
  • the clamping device may be formed, for example, as a clamping ring. It relieves the attachment of the membrane to the housing.
  • FIG. 1 carries a fuel system of an internal combustion engine overall the reference numeral 10.
  • the internal combustion engine itself is not shown in detail.
  • the fuel system 10 includes a fuel tank 12 from which an electric fuel pump 14 delivers fuel to a low pressure fuel line 16.
  • the low pressure fuel line 16 leads to a high-pressure fuel pump 18, which is shown symbolically dash-dotted lines.
  • the high-pressure fuel pump 18 comprises a delivery chamber 20, which from a in FIG. 1 Piston not shown is limited. The piston is displaced by a drive shaft, also not shown, in a reciprocating motion. The drive shaft in turn is driven by the camshaft, again not shown, of the internal combustion engine.
  • the high-pressure fuel pump 18 further comprises an inlet valve 22, which is designed as a check valve. Further, an outlet valve 24 is provided, which is also formed by a check valve.
  • the high pressure fuel pump 18 compresses the fuel to a very high pressure and delivers into a fuel rail 26 ("rail"). In this the fuel is stored under high pressure.
  • a fuel rail 26 (“rail"). In this the fuel is stored under high pressure.
  • a plurality of fuel injectors 28 are connected to the fuel manifold 26 . These inject the fuel directly into each associated combustion chambers 30 a.
  • a quantity control valve 32 is provided in order to adjust the delivery rate of the high-pressure fuel pump 18 independently of the rotational speed of the drive shaft. This is actuated by a magnetic actuator 33, which in turn is driven by a control and device, not shown.
  • the quantity control valve 32 is designed such that during a delivery stroke of the high-pressure fuel pump 18, the inlet valve 22 can be forcibly opened. As a result, the fuel under pressure in the delivery chamber 20 is not in the fuel rail 26, but back into the low-pressure fuel line 16th promoted.
  • the corresponding switching position of the quantity control valve 32 bears the reference numeral 34.
  • annular spacer 46 is arranged between the bottom portion 44 of the lower part 38 of the housing and the upper part 40 of the housing. It is welded on welds 48a and 48b firmly on the one hand with the bottom portion 44 of the lower part 38 of the housing and on the other hand with the upper part 40 of the housing.
  • annular holding portion 52 extending radially inwards on the spacer 46, two circular membranes 54a and 54b are provided which are generally circular in plan view. The attachment is made by circumferential welds 57a and 57b at the outermost edge of the membranes 54a and 54b (see. FIG. 3 ).
  • the two membranes 54a and 54b are thin-walled and made of metal, preferably stainless steel.
  • a gas volume 58 is enclosed.
  • the gas is introduced through a channel 60 provided in the annular spacer 46 (see FIG. FIG. 2 ). After the introduction of the gas into the volume 58 between the two membranes 54a and 54b, the channel 60 is closed by a ball 62.
  • the entire area between the bottom portion 44, the upper part 40 of the housing, and the spacer 46 forms a working space 66.
  • the gas volume 58 is thus arranged within the working space 66.
  • a first fluid region 64 of the working space 66 is formed between the bottom portion 44 of the lower part 38 of the housing and the lower diaphragm 54 b. Between the upper part 40 of the housing and the upper diaphragm 54a, a second fluid region 68 of the working space 66 is formed. Both fluid regions 64 and 68 may communicate with each other through a channel 70 in the annular spacer 46.
  • the two membranes 54a and 54b are of identical construction (for reasons of clarity, in FIG. 3 all the reference numerals for the upper diaphragm 54a only): At their radially outer edge they have a radially extending holding portion 72 with which they are welded to the annular spacer 54b. From the holding portion 72 of the diaphragm, a spring portion 74 bends at an angle of about 80 °. The spring portion 74 thus extends approximately in the axial direction. On the spring portion 74, in turn, a radially extending bead portion 76 is integrally formed. This is characterized by a plurality of extending beads 78. The beads 78 run concentrically about the central axis 41 of the pressure damper 36. A central region of the two membranes 54a and 54b is flat. The corresponding region in the membrane 54a is referred to as a stopper portion 80a, the corresponding area on the membrane 54b as a counter-surface 80b (see. FIG. 2 ).
  • the distance between the two diaphragms 54a and 54b and the sections 54a or 40 of the housing adjacent to them is so great that, even in the idle state, that is to say with a pressureless fuel system, a contact of the two diaphragms 54a and 54b with the corresponding sections 40 and 44 of the housing is excluded.
  • Such a limitation of the "stroke" of the membranes is possible by the use of metal as a membrane material.
  • the distance of the membranes 54 a and 54 b from the housing 40 and 44 is selected so that at a system pressure, for example, less than 100 kPa in case of pressure undershoot the membranes 54 a and 54 b, the housing 40 and 44 do not touch.
  • a system pressure for example, less than 100 kPa in case of pressure undershoot the membranes 54 a and 54 b, the housing 40 and 44 do not touch.
  • the two diaphragms 54a and 54b are moved toward each other.
  • the pressure in the gas volume 58 on the one hand and the stiffness of the two diaphragms 54a and 54b are chosen so that at normal operating pressure in the low-pressure fuel line 16, that is approximately between 0.5 and 8 bar, a contact of the two membranes 54a and 54b does not take place with each other. Pressure fluctuations can thus be easily absorbed in this normal operating range of the fuel system 10 by a corresponding movement of the two membranes 54a and 54b and a compression of the gas volume 58 and thereby damped.
  • the abutment portion 80a of the diaphragm 54a and the counter-surface 80b engage the diaphragm 54b.
  • the two membranes 54a and 54b can thus no longer move, so that an overload of the two membranes 54a and 54b can be excluded.
  • the stopper portion 80a and the mating surface 80b are machined flat or crowned.
  • the characteristic of the pressure damper 36 can also be influenced by the height of the annular spacer 46. This height in particular has an influence on the pressure at which the two diaphragms 54a and 54b come into contact with each other.
  • the internal volume can also be reduced in a targeted manner. Thereby, the effectiveness of the air spring formed by the enclosed gas volume 58 can be further increased.
  • the shape of the beads 78 and their number plays an essential role in the properties of the pressure damper 36.
  • a number of three to six beads with different bead height proved to be advantageous.
  • the bead height can vary between +/- 0.15 and 2 mm.
  • the bead may be circular, sinusoidal or spline-shaped.
  • the shape of the beads 78 and the design of the spring portion 74 ensures that the maximum stresses do not occur at the outermost edge of the two membranes 54a and 54b, but are largely evenly distributed over the diameter of the two membranes 54a and 54b.
  • FIGS. 4 and 5 and 6 are referred to.
  • a second embodiment of a pressure damper 36 is shown.
  • Such areas and elements which have equivalent functions to areas and elements of the Figures 2 and 3 illustrated embodiment, the same reference numerals. They are not explained again in detail.
  • FIGS. 4 and 5 represent pressure damper no spacer is no longer available. Instead, the top 40 and the bottom portion 44 of the housing are directly welded together. The corresponding weld bears the reference numeral 48. Accordingly, the two holding portions 72a and 72b of the two membranes 54a and 54b are welded directly together (weld seam 57).
  • FIG. 5 An in FIG. 5 only shown in dashed lines fluid connection 70, which is formed by regional breakthroughs in the clamping rings 82 and 84, the two fluid portions 64 and 68 of the working space 66 are fluidly connected to each other.
  • the openings 70 must be chosen so that the two membranes 54a and 54b are charged approximately equally.
  • FIG. 6 shows the lower membrane 54b schematically in detail.
  • A is the depth of the diaphragm 54b, it corresponds to the maximum possible stroke.
  • B denotes a transition region, and C the height of the sinking of the membrane 54b.
  • FIG. 7 is a partial section through a fuel pump shown as high-pressure fuel pump 18, for example, in the in FIG. 1 shown fuel system 10 is used. It can be seen a cylinder housing 92 with a piston 88 which limits the delivery chamber 20.
  • the quantity control valve 32 can be seen in the upper region of the fuel pump 18.
  • the outlet valve 24 is located in the left area.
  • the inlet valve 22 is formed as a spring-loaded plate valve, which can be forced by a plunger (not numbered) of the quantity control valve 32 during a delivery stroke of the piston 88 forcibly in an open position.
  • a circumferential step 94 is incorporated in the outer boundary surface of the cylinder housing 92. About this a housing sleeve 96 is pushed. By the revolving stage 94 and the Housing sleeve 96 is created around the cylinder central axis 90 annular space 66. This communicates on the one hand via a channel 100 with a low-pressure inlet 102 of the fuel pump 18. On the other hand, it communicates via a channel 104 with a pressure relief groove 106, which in a cylinder bore 108 in which the piston 88 is guided, is present.
  • annular space 66 In the annular space 66, two annular peripheral membranes 54a and 54b are arranged. Whose outer edges are welded via welds 57a to 57d on the one hand with the cylinder housing 92 and the other with the housing sleeve 96. This creates two separate gas volumes 58a and 58b. Between these there is a fluid region 64 of the working space 66, which in particular communicates via the channel 100 with the low-pressure inlet 102.
  • the annular space 66 and the gas volumes 58a and 58b in this way form a pressure damper 36, which is arranged coaxially with the cylinder central axis 90 of the high-pressure fuel pump 18.
  • FIG. 8 a modified embodiment of such an annular pressure damper 36 is shown.
  • pressure damper 36 carry such elements and areas, which equivalent functions to elements and areas of the in the FIGS. 7 have shown pressure damper 36, the same reference numerals. They are not explained again in detail.
  • the pressure damper 36 which in FIG. 8 is shown, comprises a flattened metal tube 54, which is sealed gas-tight at the ends. Its interior forms a gas volume 58.
  • the metal tube 54a is wound in the working space 66 in a spiral and helical manner coaxially with the central cylinder axis 90. As a result, it is on the one hand with respect to the housing sleeve 96 and the other with respect to the in FIG. 8 upper and lower end surfaces of the working space 66 under a bias and is thereby fixed.
  • FIG. 9 a further variant of a pressure damper 36 is shown.
  • elements and regions which have equivalent functions to elements and regions which have already been explained in connection with the preceding figures bear the same reference numerals. Normally they will not be explained again in detail.
  • the pressure damper 36 shown is in the left half of FIG. 9 differently designed than on the right half. Both devices 36 have in common that they have only a single membrane 54. This is welded in the region of its holding portion 72 in 57 with the upper part 40 of the housing. Unlike the example in the Figures 2 and 3 Membrane has the in FIG. 9 illustrated diaphragm 54 a bellows portion 110 which is disposed between the bead portion 76 and the holding portion 72 and is composed of individual segments 110a to 110d. This bellows portion 110 allows a comparatively large volume change of the gas volume 58 enclosed by the diaphragm 54 and the housing 40.
  • the gas volume 58 is thereby reduced overall in that between the membrane 54 and the upper part 40 of the housing, a packing 112 is attached to the upper part 40 of the housing.
  • a stopper portion 80a extends from the bead portion 76 of the diaphragm 54 to the lower portion 38 of the housing, whereas in the right half of the FIG. 9 the stopper portion 80a extends toward the packing 112.
  • Lower part 38 of the housing as a counter surface 80b for the stopper portion 80a.
  • the gas volume 58 trapped by the membrane 54 is filled with helium. This is under an overpressure, which corresponds to approximately half of the maximum operating pressure, minus the pressure increase caused by the compression of the diaphragm 54.
  • a magnetic metal material is used for the membrane 54.
  • the pressure damper 36 acts similarly as a "dust catcher", because through them magnetic dirt particles are trapped from the fluid and their distribution in the fluid system 10 is prevented.
  • FIG. 10 shown An alternative to this is in FIG. 10 shown.
  • the in FIG. 10 shown pressure damper 36 differs from that in FIG. 9 shown by the fact that instead of a separate packing 112 in the upper part 40 of the housing, a deep-drawn section 112 is present, which on the one hand reduces the trapped gas volume 58 and on the other has the counter surface 80b, which cooperates with the stopper portion 80a of the diaphragm 54.
  • FIG. 11 again shows an embodiment in which a separate filler body 112 is present, which is not hollow, but solid and, moreover, in a the stopper portion 80a of the diaphragm 54 facing portion 116 has a smaller diameter.
  • the contour of the filling body 112 of FIG. 11 something adapted to the contour of the membrane 54, so that the corresponding gas volume 58 is particularly low.
  • FIG. 12 an embodiment is shown in which two membranes 54a and 54b are present, corresponding to, for example, the in FIG. 4 shown embodiment of a pressure damper 36.
  • FIG. 12 In contrast to FIG. 4 is at the in FIG. 12
  • the in FIG. 12 shown pressure damper has - analogous to that in the FIGS. 4 and 5 shown - upper and lower clamping rings 82 and 84, which, however, in figure 12 are shown only schematically.
  • the hydraulically effective area of the membranes 54a and 54b is maximized, which can be used to reduce the overall size of the pressure damper 36.
  • the clamping rings 82 and 84 are supported by spring portions 118 and 120 on the upper part 40 and on the lower part 38 of the housing. In this way, manufacturing tolerances of the membranes 54a and 54b can be compensated.
  • a disc-shaped retaining ring 122 is clamped, which has a central opening 124.
  • a two-part packing 112 is inserted, and the retaining ring 122 is clamped between the two halves 112a and 112b of the packing 112.
  • a circumferential groove is present, into which the edge of the opening 124 of the retaining ring 122 engages.
  • a one-piece design of the retaining ring 122 with the packing 112 is conceivable.
  • FIG. 13 Yet another variant of a pressure damper 36 is in FIG. 13 shown.
  • this pressure damper 36 no filler is present, so that this device is constructed similar to those in the FIGS. 4 and 5 is shown.
  • the differences relate in particular to the clamping rings 82 and 84, with which the membranes 54a and 54b are held on the housing 40 and 38:
  • the clamping rings 82 and 84 have cantilevered spring portions, wherein a spring portion 118a and 120a, the membranes 54a and 54b in FIG. 13 positioned in the vertical direction, whereas a spring portion 118b and 120b, the two membranes 54 and 56 in FIG. 13 positioned or centered in the horizontal direction.
  • the spring sections 118a and 120a are formed by individual radially inwardly facing brackets of the two clamping rings 82 and 84, which in the in FIG. 13 shown mounting position against the upper part 40 and the lower part 38 of the housing are biased.
  • the spring sections 118b and 120b are formed by individual radially outwardly acting brackets which abut against the inner circumferential surface of the upper part 40 of the housing 40 and are biased against it.
  • FIG. 14 a further modified embodiment of a pressure damper 36 is shown.
  • a tubular mounting portion 122 is present at the radially outer edge of the bead portion 76, which extends approximately parallel to the central axis 41 of the pressure damper 36 and is welded in its edge 57 with the housing 40.
  • the membrane 54 is attached directly to the housing 40, which saves otherwise required additional designs.
  • the pressure damper 36 in FIG. 14 a clamping ring 124, which presses the mounting portion 122 from radially inwardly against the housing 40.
  • the weld 57 is mechanically relieved.
  • the radially maximum outer weld 57 allows the use of the entire inner diameter of the housing 40 as a hydraulically effective diameter. This lowers the manufacturing costs.
  • the gas volume 58 can be established either during the production of the weld seam 57 (welding in a pressure chamber). Or the working space 66 is subsequently filled via the opening 60, which is then closed by the element 62. The latter can be welded to the housing 40, for example. As in the embodiments of the FIGS. 9 to 11 is also at the in FIG. 14 shown pressure damper 36, the gas volume 58th formed between the diaphragm 54 and the housing 40. This leads to a minimization of the required installation space.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Diaphragms And Bellows (AREA)
  • Reciprocating Pumps (AREA)
  • Pipe Accessories (AREA)

Claims (15)

  1. Dispositif (36) pour l'atténuation des pulsations de pression dans un système fluidique (16), en particulier dans un système de carburant d'un moteur à combustion interne, comprenant un boîtier (38, 40) et au moins un espace de travail (66) qui communique au moins en partie avec le système fluidique (16), au moins un volume de gaz (58) fermé de manière étanche par une membrane (54) étant prévu à l'intérieur de l'espace de travail (66), caractérisé en ce que la membrane (54) est en métal et la membrane (54) et/ou le boîtier (38, 40) sont au moins en partie magnétiques.
  2. Dispositif (36) selon la revendication 1, caractérisé en ce que la membrane est limitée par un tube métallique (54) à paroi mince et fermé de manière étanche aux gaz à ses extrémités.
  3. Dispositif (36) selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une paroi extérieure de l'espace de travail est également réalisée sous forme de membrane.
  4. Dispositif (36) selon l'une quelconque des revendications précédentes, caractérisé en ce que le volume de gaz inclus (58) présente une pression définie, de préférence une surpression, pour une pression extérieure normale.
  5. Dispositif (36) selon la revendication 4, caractérisé en ce que le volume de gaz (58) présente une ouverture refermable (60), par le biais de laquelle la pression peut être ajustée.
  6. Dispositif (36) selon l'une quelconque des revendications précédentes, caractérisé en ce que le volume de gaz inclus (58) est réduit par une région de remplissage (112).
  7. Dispositif (36) selon l'une quelconque des revendications précédentes, caractérisé en ce que le volume de gaz (58) est limité par au moins deux membranes (54a, 54b) qui sont tendues dans la région de leurs bords (82, 84).
  8. Dispositif (36) selon la revendication 7, caractérisé en ce que les membranes (54a, 54b) sont dans l'ensemble essentiellement parallèles.
  9. Dispositif (36) selon la revendication 8, caractérisé en ce que le volume de gaz (58) est formé entre les deux membranes (54a, 54b) et les deux membranes (54a, 54b) présentent chacune au moins une surface de butée (80a) ou une surface conjuguée (80b) qui sont en contact dans le cas d'une déviation maximale des deux membranes (54a, 54b).
  10. Dispositif (36) selon l'une quelconque des revendications 7 à 9, caractérisé en ce que les bords des deux membranes (54a, 54b) sont connectés hermétiquement l'un à l'autre et sont serrés (82, 84) radialement à l'intérieur de la ligne d'étanchéité (57).
  11. Dispositif (36) selon la revendication 10, caractérisé en ce que le serrage (82, 84) dispose d'une élasticité constructive (118, 120).
  12. Dispositif (36) selon l'une quelconque des revendications 7 à 11, caractérisé en ce que les deux membranes (54a, 54b) sont identiques.
  13. Dispositif (36) selon l'une quelconque des revendications 7 à 12, caractérisé en ce que l'espace de travail (66) est divisé par les deux membranes (54a, 54b) en deux régions (64, 68) qui communiquent l'une avec l'autre par une liaison fluidique (70).
  14. Dispositif (36) selon l'une quelconque des revendications 7 à 13, caractérisé en ce qu'entre les deux membranes (54a, 54b) est prévu un élément d'espacement annulaire (46).
  15. Dispositif (36) selon les revendications 12 et 14, caractérisé en ce que la liaison fluidique (70) est réalisée dans l'élément d'espacement.
EP10180722A 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne Expired - Lifetime EP2278150B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10248822 2002-10-19
DE10327408.1A DE10327408B4 (de) 2002-10-19 2003-06-18 Vorrichtung zum Dämpfen von Druckpulsationen in einem Kraftstoffsystem einer Brennkraftmaschine
EP03015623A EP1411236B1 (fr) 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP03015623.6 Division 2003-07-16
EP03015623A Division-Into EP1411236B1 (fr) 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
EP03015623A Division EP1411236B1 (fr) 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2278150A1 EP2278150A1 (fr) 2011-01-26
EP2278150B1 true EP2278150B1 (fr) 2012-10-10

Family

ID=32049457

Family Applications (3)

Application Number Title Priority Date Filing Date
EP10180727A Expired - Lifetime EP2284384B1 (fr) 2002-10-19 2003-07-16 Dispositif d'amortissement d'impulsions de pression dans un système de fluide, notamment dans un système de carburant d'un moteur à combustion interne
EP10180742.8A Expired - Lifetime EP2278151B1 (fr) 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
EP10180722A Expired - Lifetime EP2278150B1 (fr) 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP10180727A Expired - Lifetime EP2284384B1 (fr) 2002-10-19 2003-07-16 Dispositif d'amortissement d'impulsions de pression dans un système de fluide, notamment dans un système de carburant d'un moteur à combustion interne
EP10180742.8A Expired - Lifetime EP2278151B1 (fr) 2002-10-19 2003-07-16 Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne

Country Status (3)

Country Link
EP (3) EP2284384B1 (fr)
DE (3) DE10327408B4 (fr)
ES (4) ES2393308T3 (fr)

Families Citing this family (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008032676B4 (de) * 2008-07-12 2019-10-02 Obrist Engineering Gmbh Feder-/Aktuatorelement, Feder-/Aktuatoranordnung sowie Verfahren zu deren Herstellung und Steuerelement für ein Ventil
DE102008043217A1 (de) * 2008-10-28 2010-04-29 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe für eine Brennkraftmaschine
DE102010011292A1 (de) 2010-03-13 2011-09-15 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kraftstoffhochdruckpumpe
DE102011053358A1 (de) 2011-09-07 2013-03-07 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Kraftstoffpumpe
DE102013218713A1 (de) 2013-09-18 2015-03-19 Robert Bosch Gmbh Hochdruckpumpe für ein Kraftstoffeinspritzsystem, Kraftstoffeinspritzsystem
DE102013220911A1 (de) * 2013-10-15 2014-11-27 Continental Automotive Gmbh Ausgleichsbehälter und Pumpenvorrichtung
DE102014202809A1 (de) 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014202796A1 (de) 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014202794A1 (de) 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014202795A1 (de) 2014-02-17 2015-08-20 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014219199A1 (de) * 2014-09-23 2016-03-24 Robert Bosch Gmbh Kraftstoffinjektor
DE102014222417B4 (de) 2014-11-03 2022-03-17 Vitesco Technologies GmbH Kraftstofffördereinheit
DE102014226304A1 (de) 2014-12-17 2016-06-23 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014226316A1 (de) 2014-12-17 2016-06-23 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102015203345A1 (de) * 2015-02-25 2016-08-25 Robert Bosch Gmbh Pumpe, insbesondere Kraftstoffhochdruckpumpe
JP6534832B2 (ja) 2015-03-06 2019-06-26 株式会社ケーヒン 燃料供給装置及びベローズ式ダンパ
DE102015219537A1 (de) * 2015-10-08 2017-04-27 Robert Bosch Gmbh Membrandose zum Dämpfen von Druckpulsationen in einem Niederdruckbereich einer Kolbenpumpe
DE102015219772A1 (de) * 2015-10-13 2016-10-06 Continental Automotive Gmbh Niederdruckdämpfer sowie Kraftstoffhochdruckpumpe
DE102015219769A1 (de) * 2015-10-13 2016-10-06 Continental Automotive Gmbh Niederdruckdämpfer sowie Kraftstoffhochdruckpumpe
DE102016200232A1 (de) * 2016-01-12 2017-07-13 Continental Automotive Gmbh Kraftstoffeinspritzsystem
DE102016201082B4 (de) 2016-01-26 2017-10-05 Continental Automotive Gmbh Kraftstoffhochdruckpumpe
DE102016203217B4 (de) * 2016-02-29 2020-12-10 Vitesco Technologies GmbH Dämpferkapsel, Druckpulsationsdämpfer und Kraftstoffhochdruckpumpe
DE102016205428A1 (de) * 2016-04-01 2017-10-05 Robert Bosch Gmbh Druckdämpfungseinrichtung für eine Fluidpumpe, insbesondere für eine Hochdruckpumpe eines Kraftstoffeinspritzsystems
DE102016212458A1 (de) * 2016-07-08 2018-01-11 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
DE102017000618A1 (de) 2017-01-24 2018-07-26 Daimler Ag Dämpfungseinrichtung, insbesondere für ein Fahrzeug
GB2559612B (en) * 2017-02-13 2020-04-01 Delphi Tech Ip Ltd Damper device with a capsule held in a rubber holder maintained in position by a metallic plug
DE102017203762A1 (de) 2017-03-08 2018-09-13 Continental Automotive Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
DE102018200146B4 (de) * 2018-01-08 2019-11-28 Continental Automotive Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
DE102018204555A1 (de) * 2018-03-26 2019-09-26 Continental Automotive Gmbh Kraftstoffhochdruckpumpe für ein Kraftstoffeinspritzsystem
IT201800004282A1 (it) * 2018-04-06 2019-10-06 Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
DE102018211301A1 (de) 2018-07-09 2020-01-09 Robert Bosch Gmbh Druckdämpfer für eine Kraftstoff-Hochdruckpumpe
JP7041956B2 (ja) * 2018-09-20 2022-03-25 株式会社不二工機 パルセーションダンパー
DE102019101135A1 (de) 2019-01-17 2020-07-23 Bayerische Motoren Werke Aktiengesellschaft Brennkraftmaschine mit einem Kraftstoffeinspritzsystem
US10969049B1 (en) * 2019-09-27 2021-04-06 Robert Bosch Gmbh Fluid damper
CN115218057A (zh) * 2022-07-28 2022-10-21 德帕姆(杭州)泵业科技有限公司 一种脉动阻尼器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3366144A (en) * 1965-10-18 1968-01-30 Diatemp Inc High pressure control diaphragm
US5794594A (en) * 1995-08-30 1998-08-18 Robert Bosch Gmbh Fuel injection pump
EP0950809A2 (fr) * 1998-04-15 1999-10-20 Mitsubishi Denki Kabushiki Kaisha Accumulateur à haute pression
US6079450A (en) * 1999-02-26 2000-06-27 Mitsubishi Denki Kabushiki Kaisha Metal diaphragm type pulsation absorber for high-pressure fuel pump
EP1342911A2 (fr) * 2002-03-04 2003-09-10 Hitachi, Ltd. Système d'alimentation de carburant

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3035613A (en) * 1958-08-08 1962-05-22 Chiksan Co Pulsation dampener
DE3152861C2 (de) * 1981-05-14 1983-12-01 Robert Bosch Gmbh, 7000 Stuttgart Dämpferelement
WO1986002424A1 (fr) * 1984-10-16 1986-04-24 W. Rast Pty. Ltd. Coussinets d'absorption des chocs dus a la pression et leur procede de fabrication
US5562429A (en) * 1989-09-28 1996-10-08 Caro Manufacturing Corporation Pulse dampener and fuel pump having same
JPH08261096A (ja) * 1995-03-23 1996-10-08 Nhk Spring Co Ltd 液圧サージ吸収装置およびそのベローズアッセンブリ
DE19539885A1 (de) * 1995-05-26 1996-11-28 Bosch Gmbh Robert Kraftstoffversorgungsanlage und Verfahren zum Betreiben einer Brennkraftmaschine
JPH10299609A (ja) * 1997-04-18 1998-11-10 Zexel Corp 脈動低減用ダンパ
US6418909B2 (en) * 1998-11-24 2002-07-16 Robert Bosch Corporation Low cost hydraulic damper element and method for producing the same
DE10005588A1 (de) * 2000-02-09 2002-03-28 Bayerische Motoren Werke Ag Schwingungsdämpfer für eine hydraulische Fahrzeug-Bremsanlage
JP3217775B2 (ja) * 2000-02-29 2001-10-15 三桜工業株式会社 フューエルデリバリパイプ
DE10016880A1 (de) * 2000-04-05 2001-10-18 Bayerische Motoren Werke Ag Schwingungsdämpfer für eine hydraulische Fahrzeug-Bremsanlage
NL1016384C2 (nl) * 2000-10-11 2002-04-12 Helvoet B V Dempingsinrichting met ten minste gedeeltelijk flexibel beweegbaar uitgevoerd membraan.
US6513500B2 (en) * 2001-04-02 2003-02-04 Delphi Technologies, Inc. Fuel rail damping device

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3366144A (en) * 1965-10-18 1968-01-30 Diatemp Inc High pressure control diaphragm
US5794594A (en) * 1995-08-30 1998-08-18 Robert Bosch Gmbh Fuel injection pump
EP0950809A2 (fr) * 1998-04-15 1999-10-20 Mitsubishi Denki Kabushiki Kaisha Accumulateur à haute pression
US6079450A (en) * 1999-02-26 2000-06-27 Mitsubishi Denki Kabushiki Kaisha Metal diaphragm type pulsation absorber for high-pressure fuel pump
EP1342911A2 (fr) * 2002-03-04 2003-09-10 Hitachi, Ltd. Système d'alimentation de carburant

Also Published As

Publication number Publication date
EP2284384A2 (fr) 2011-02-16
ES2528601T3 (es) 2015-02-10
DE10362412B3 (de) 2017-09-07
EP2278150A1 (fr) 2011-01-26
DE10327408A1 (de) 2004-04-29
EP2284384B1 (fr) 2012-10-10
EP2278151A1 (fr) 2011-01-26
DE10362411B3 (de) 2017-09-07
EP2278151B1 (fr) 2015-01-14
ES2393308T3 (es) 2012-12-20
ES2391727T3 (es) 2012-11-29
EP2284384A3 (fr) 2011-03-23
DE10327408B4 (de) 2017-10-26
ES2391627T3 (es) 2012-11-28

Similar Documents

Publication Publication Date Title
EP2278150B1 (fr) Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
EP1411236B1 (fr) Dispositif pour l'atténuation des pulsations de pression dans un système de fluide, en particulier dans un système de carburant d'un moteur à combustion interne
EP1834089B1 (fr) Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne
EP2273115B1 (fr) Pompe à fluide, en particulier pompe à carburant haute pression, avec amortisseur de pression
EP1411238B1 (fr) Soupape de limitation de pression pour un système d'injection de carburant
EP2748439B1 (fr) Système de dosage pour un agent de réduction liquide
EP2519744B1 (fr) Pompe ayant une valve avec un dispositif d'amortissement
DE102016203217B4 (de) Dämpferkapsel, Druckpulsationsdämpfer und Kraftstoffhochdruckpumpe
DE102004013307A1 (de) Kraftstoffhochdruckpumpe mit einem Druckbegrenzungsventil
DE102004002489B4 (de) Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe
DE102004047601A1 (de) Fluidpumpe, insbesondere Kraftstoff-Hochdruckpumpe
EP1403509B1 (fr) Dispositif de limitation de pression et système de combustible avec tel dispositif de limitation de pression
WO2010102850A1 (fr) Soupape d'aspiration pour une pompe haute pression de carburant
EP0641935B1 (fr) Pompe à membrane à entraînement hydraulique avec limitation mécanique de la course de la membrane
EP2007979A1 (fr) Pompe à piston radial pour l'alimentation haute pression en carburant d'un moteur à combustion interne
DE112020000261T5 (de) Metalldämpfer mit Metallmembran und damit versehene Kraftstoffpumpe
WO2017102151A1 (fr) Pompe à fluide, en particulier pompe à carburant haute pression
EP1022460B1 (fr) Méthode de montage
WO2019134990A1 (fr) Pompe à carburant haute pression pour système d'injection de carburant
DE102004064240B3 (de) Fluidpumpe mit integriertem Druckdämpfer
WO2023036646A1 (fr) Pompe à fonctionnement cyclique, en particulier pompe à piston à carburant haute pression
DE102009045230A1 (de) Druckbegrenzungseinrichtung
WO2007071661A1 (fr) Pompe haute pression comprenant plusieurs pistons par cylindre

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: 1411236

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR IT

17P Request for examination filed

Effective date: 20110726

17Q First examination report despatched

Effective date: 20111111

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AC Divisional application: reference to earlier application

Ref document number: 1411236

Country of ref document: EP

Kind code of ref document: P

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR IT

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2391627

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20121128

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 50314538

Country of ref document: DE

Effective date: 20121206

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

26N No opposition filed

Effective date: 20130711

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 50314538

Country of ref document: DE

Effective date: 20130711

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

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

Ref country code: IT

Payment date: 20220729

Year of fee payment: 20

Ref country code: ES

Payment date: 20220819

Year of fee payment: 20

Ref country code: DE

Payment date: 20220927

Year of fee payment: 20

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

Ref country code: FR

Payment date: 20220725

Year of fee payment: 20

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230509

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 50314538

Country of ref document: DE

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20230728

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20230717