EP1411236A2 - 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

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Publication number
EP1411236A2
EP1411236A2 EP03015623A EP03015623A EP1411236A2 EP 1411236 A2 EP1411236 A2 EP 1411236A2 EP 03015623 A EP03015623 A EP 03015623A EP 03015623 A EP03015623 A EP 03015623A EP 1411236 A2 EP1411236 A2 EP 1411236A2
Authority
EP
European Patent Office
Prior art keywords
membrane
gas volume
membranes
pressure
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.)
Granted
Application number
EP03015623A
Other languages
German (de)
English (en)
Other versions
EP1411236B1 (fr
EP1411236A3 (fr
Inventor
Helmut Rembold
Wolfgang Bueser
Albrecht Baessler
Klaus Lang
Marcus Wuenning
Weidong Qi
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
Priority claimed from DE10327408.1A external-priority patent/DE10327408B4/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to EP10180722A priority Critical patent/EP2278150B1/fr
Priority to EP10180727A priority patent/EP2284384B1/fr
Priority to EP10180742.8A priority patent/EP2278151B1/fr
Publication of EP1411236A2 publication Critical patent/EP1411236A2/fr
Publication of EP1411236A3 publication Critical patent/EP1411236A3/fr
Application granted granted Critical
Publication of EP1411236B1 publication Critical patent/EP1411236B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus 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
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0041—Means for damping pressure pulsations
    • 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
    • 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
    • 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

Definitions

  • the invention relates to a device for damping of 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 at least partially communicates with the fluid system.
  • Such a device is known from DE 195 39 885 A1 known.
  • a fuel system one Internal combustion engine with direct fuel injection shown.
  • the fuel is too promoted a high-pressure piston pump, which the Fuel is compressed to a very high pressure.
  • the High-pressure piston pump the fuel enters a Fuel rail ("Rail").
  • the high pressure piston pump is from a camshaft of Internal combustion engine driven.
  • Quantity control valve provided to the flow rate of the High-pressure piston pump regardless of the speed of the To be able to adjust the camshaft.
  • a pressure damper Around to dampen, there is provided a pressure damper. This consists of a housing and a piston, which of a spring is biased.
  • the present invention therefore has the object, a Device of the type mentioned in the above way, that they are in a variable-pressure fuel system can be used, but it builds small and a has a long service life.
  • the Membrane is made of metal.
  • Such a membrane has various advantages: First, such a membrane compared to conventional gases and also to fluids very tight. Here plays in particular the high tightness of Metal membranes a positive over HC emissions Role. On the other hand occurs in a metal diaphragm also low pressures, for example, when switched off Internal combustion engine, over time no overstretching, so that a damper device with a metal diaphragm in a fluid system can be used, which has a in having a wide range of variable fluid pressure.
  • At least one outer wall of the work space also is designed as a membrane, you get on a minimum Space an additional hydraulically effective area.
  • the Effectiveness of the device according to the invention is This again significantly increased, at the same time small footprint.
  • the enclosed Gas volume at a standard external pressure has a defined pressure, preferably one Overpressure.
  • a defined pressure preferably one Overpressure.
  • the "Spring stiffness" can be adjusted.
  • an overpressure in the trapped gas volume in the Comparison to the external pressure are chosen, because thereby can the whole possible voltage range (train and pressure) be exploited of the membrane material.
  • a negative pressure or standard pressure Preferably, such an internal overpressure is selected, which is about half of the maximum Operating pressure, minus the pressure increase caused by the compression of the component arises, corresponds.
  • the gas volume can be a closable opening have, over which the pressure can be adjusted. This facilitates the production of gas volume. Otherwise would have to manufacture itself at a certain pressure respectively.
  • the membrane has at least one bead.
  • a bead By such a bead can the spring properties of the membrane itself and also their strength properties significantly influenced become. With a bead, the membrane can thus optimally adapted to the individual requirements of the fluid system become. Above all, the damper with comparable Construction volume have even more damping volume, or alternatively be built smaller.
  • the beads can different height and / or a different one Course and / or have a different cross-section.
  • the beads can also be shaped so that the maximum stress does not occur at the edge of the membrane, and the mechanical stresses over the surface of the membrane distributed as evenly as possible. Furthermore, can by a corresponding membrane design the entire Material bandwidth in the tensile and compressive stress range be used.
  • the membrane at least has a stop area, which at a maximum Deflection of the membrane with a counter surface in plant comes.
  • the maximum deflection is chosen so that Damage to the membrane, such as a plastic deformation, just barely avoided.
  • the Counter surface on the housing, on a separate Stop member, and / or on another membrane is trained.
  • the overload protection can so on realized various very simple and inexpensive types become.
  • the stop surface on the housing for example be made by deep drawing, which is very simple and is inexpensive.
  • a separate stop part is inexpensive, taking for a same damper different stop parts can be provided so that the same device easily adapted to different Operating conditions can be adjusted.
  • the Stop surface on another membrane again saves Space.
  • the trapped gas volume through a filling area is reduced.
  • This filling area can also by the stopper (this then acts as a "filler") or a housing portion are formed.
  • the stopper this then acts as a "filler"
  • a housing portion are formed.
  • An advantageous embodiment of the invention Device is that the gas volume through At least two membranes are limited in the area their edges are clamped. Such a pressure damper builds comparatively flat. All the more so if the Membranes are substantially parallel. It is Basically, of course, conceivable that the gas volume in the between the two membranes lying space at their Merging is introduced so that on one Be Shellö réelle can be dispensed with.
  • the clamping has a constructive elasticity.
  • a retaining ring made of a rubber elastic material can be used or it can a metal bracket can be used which has a Has spring section.
  • This is on the one hand a safe Fixation of the membranes achieved, and on the other hand can Manufacturing tolerances are compensated. in principle can attack the restraint at any point on the membrane, However, an approach in the area of a particularly favorable Center plane of the two membranes.
  • the space of the device according to the invention is particularly small if the working space of the two membranes in two Fluid areas is divided, which by a Communicate fluid communication with each other.
  • the inventive Damping device accommodated particularly space-saving be when the workspace includes an annulus and the Gas volume is also annular. Especially advantageous It is when the work space and the gas volume a cylinder of a fuel pump at least approximately are arranged coaxially with the cylinder axis.
  • the pressure damper surrounds so to speak the cylinder and in this existing piston, which additionally one more Noise damping causes.
  • the effective area of the gas volume can be increased again when the spiral gas volume is helical extends in the axial direction of the working space.
  • Another preferred embodiment of the invention Device is characterized in that the gas volume filled with helium. This facilitates the detection a leak.
  • the membrane and / or the housing may be magnetic be.
  • appropriate manufacturing process For example, mechanical rolling and embossing
  • forming martensite Material martensitic structure
  • the device in the fluid capture existing magnetic dirt particles and their prevent further distribution. This increases the Reliability of the components present in the fluid system, for example, a pump.
  • costs are saved, because the time-consuming demagnetization of the component is eliminated.
  • no directly adjacent and relatively movable parts are present, cause the trapped dirt particles no Functional damage to the device.
  • the membrane of a Band material is produced, which residual stresses having. Such residual stresses lead during the Forming process to a flat distortion, so that the Material in the deformed state is discarded.
  • This one can now targeted for the simplification of the production of Membrane can be used, especially if this Having at least one Faltenbalgabites: Due to the Delay is namely a deliberate separation of the unpressurized state flat contiguous areas 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 become the individual sections ("segments") of the membrane superimposed and in a welding device "Stacked”. After closing the welding device is whose interior evacuated and with filling gas, for example with helium, filled with a desired pressure. In this Phase is through the warped membrane sections Ensure that the filling gas is safe in all cavities flows. Then the individual sections pressed together and welded together.
  • filling gas for example with helium
  • the Device according to the invention comprises the membrane at least one bead section and at least one Bellows. This allows the combination of Advantages of both versions.
  • the membrane at its radial outer edge has a fastening portion, which extends approximately parallel to the central axis and on the Housing is attached. In this way, the entire Inner diameter of the housing used hydraulically effective be, which minimizes the required space and the Costs lowers.
  • the device a Clamping device comprising the attachment portion acted upon radially against the housing.
  • the clamping device may be formed, for example, as a clamping ring. By it relieves the attachment of the membrane to the housing.
  • a fuel system carries a Internal combustion engine as a whole the reference numeral 10. Die 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 the Fuel in a low pressure fuel line 16 promotes.
  • the low pressure fuel line 16 leads to a high pressure fuel pump 18, which symbolically dash-dotted lines is shown.
  • the high-pressure fuel pump 18 comprises a delivery chamber 20, of a piston, not shown in Figure 1 is limited.
  • the piston will not work either way shown drive shaft in a reciprocating motion added.
  • the drive shaft in turn will turn from the turn not shown camshaft of the internal combustion engine driven.
  • the high pressure fuel pump 18 includes Further, an inlet valve 22, which serves as a check valve is trained. Furthermore, an outlet valve 24 is present, which is also formed by a check valve.
  • the high pressure fuel pump 18 compresses the fuel at a very high pressure and pump into a fuel rail 26 ("Rail"). In this is the fuel stored under high pressure.
  • a fuel rail 26 (“Rail").
  • To the fuel manifold 26 are multiple fuel injectors 28 connected. These inject the Fuel directly in each associated combustion chambers 30 on.
  • a quantity control valve 32 is provided to the flow rate of the high pressure fuel pump 18th regardless of the speed of the drive shaft to adjust can.
  • This is actuated by a magnetic actuator 33, which in turn controlled by a control and device, not shown becomes.
  • the quantity control valve 32 is designed such that during a delivery stroke of the high-pressure fuel pump 18th the inlet valve 22 can be forcibly opened. As a result, the standing under pressure in the delivery chamber 20 Fuel not in the fuel rail 26, but back into the low pressure fuel line 16 promoted.
  • the corresponding switching position of Quantity control valve 32 is designated 34.
  • the thereby in the low-pressure fuel line 16 initiated pressure pulsations are from a device damped to dampen pressure pulsations.
  • the pressure damper 36 is constructed as follows (see Figures 2 and 3):
  • the pressure damper 36 comprises a housing with a lower part 38 and an upper part 40.
  • the lower part 38 has in the in Figure 2 shown cut mushroom-shaped, so it is substantially rotationally symmetric with a central axis 41. It comprises an installation section 42 with an in this centrally introduced inlet channel 43 and a overall plate-shaped and in plan view circular bottom portion 44, the overall level in is approximately at a right angle to the central axis 41.
  • the Top 40 of the housing is also plate-shaped and in the plan view formed circular.
  • annular spacer 46 Between the bottom portion 44 of the lower part 38 of the Housing and the upper part 40 of the housing is a annular spacer 46 is arranged. He is over 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 welded to the upper part 40 of the housing. At one on the spacer 46 radially inwardly extending annular holding portion 52 are two in total in plan view circular membranes 54a and 54b attached. The attachment is made by circulating Welds 57a and 57b at the outermost edge of the membranes 54a and 54b (see Figure 3). The two membranes 54a and 54b are thin-walled and made of metal, preferably made of Stainless steel.
  • a gas volume 58 locked in Between the upper diaphragm 54a and the lower diaphragm 54b and the spacer 46 is a gas volume 58 locked in.
  • the gas is passed through a channel 60 introduced in the annular spacer 46th is present (see Figure 2).
  • the channel 60 After the introduction of the Gas in the volume 58 between the two membranes 54a a 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 within the working space 66 is arranged.
  • 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 membrane 54b. Between the Top 40 of the housing and the upper membrane 54a is a second fluid region 68 of the working space 66 is formed. Both Fluid areas 64 and 68 may pass through a channel 70 in FIG annular spacers 46 communicate with each other.
  • the two membranes 54a and 54b are constructed identically (For reasons of clarity, in FIG the upper membrane 54a has all reference numerals inscribed): An their radially outer edge they have a radial extending holding portion 72, with which they on annular spacers 54b are welded. From Holding portion 72 of the membrane bends a spring portion 74th at an angle of about 80 °. The spring portion 74 thus runs approximately in the axial direction. To the Spring section 74 is again a radially extending Bead portion 76 integrally formed. This one stands out a plurality of extending beads 78. The beads 78 run concentrically around the central axis 41 of the Pressure damper 36. A central area of the two Diaphragms 54a and 54b are flat. Of the corresponding area at the diaphragm 54a is called Stopper portion 80a denotes the corresponding area on the membrane 54b as counter-surface 80b (see Figure 2).
  • the pressure damper 36 operates as follows:
  • the pressure damper can basically arbitrarily arranged in the room) of the Working space 66 with the low pressure fuel line 16.
  • the upper fluid region 68 communicates the working space 66 in turn with the lower fluid area 64.
  • Within the workroom 66 is that of the two Membranes 54a and 54b and the annular spacer 46 limited gas volume 58 available. This is in the Hibernation of the fuel system 10 under a light Overpressure to the outside atmosphere. Through this Overpressure, the bead portion 76 and the Stopper portion 80a and the mating surface 80b of the two Membranes 54a and 54b slightly bulging outwards.
  • the distance between the two membranes 54a and 54b and the adjacent to them sections 54a and 40 of the Housing is so big that even when at rest, so with pressureless fuel system, a touch of the two Membranes 54a and 54b with the corresponding sections 40th and 44 of the housing is excluded.
  • Such Limitation of the "stroke" of the membranes is due to the Use of metal as membrane material possible.
  • the distance between the membranes 54 a and 54 b from the housing 40 or 44 is chosen so that at a system pressure for example, less than 100 kPa in case of pressure undershoot the membranes 54a and 54b the housing 40th or do not touch 44. This is the damping function of Pressure damper 36 also still in this Cellrytician Guaranteed pressure range.
  • the electric fuel pump 14 so with a specific Pressure promotes the two membranes 54a and 54b moved towards each other.
  • the pressure in the gas volume 58 on the one hand and the rigidity of the two membranes 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 touch of the two membranes 54a and 54b does not take place with each other. Pressure fluctuations can thus in this normal operating range of the Fuel system 10 by a corresponding movement of the both membranes 54a and 54b and a compression of the Gas volume 58 easily recorded and thereby be steamed.
  • the Characteristic of the pressure damper 36 also by the height of the annular spacer 46 are influenced. These Height in particular has an influence on the pressure at which the two membranes 54a and 54b abutting each other come.
  • the internal volume also targeted be downsized. This can increase the effectiveness of the enclosed gas volume 58 formed air spring be further increased.
  • the shape of the beads 78 and their number plays a essential role for the properties of the pressure damper 36.
  • a membrane with a diameter of 30 - 60 mm and a wall thickness of 0.2 - 1.0 mm has a number from three to six beads with different bead heights proved to be advantageous.
  • the bead height can be vary between +/- 0.15 and 2 mm.
  • the bead can thereby be circular, sinusoidal or spline-shaped.
  • FIG. 4 and 5 and 6 In this is a second embodiment of a Pressure damper 36 shown. In doing so, carry such areas and elements which have equivalent functions to areas and elements of the illustrated in Figures 2 and 3 Embodiment, have the same reference numerals. They are not explained again in detail.
  • Fluid connection 70 which by regions breakthroughs is formed in the clamping rings 82 and 84, the two fluid areas 64 and 68 of the working space 66 fluidly connected.
  • the breakthroughs 70 must be chosen so that the two membranes 54a and 54b are charged approximately the same.
  • FIG. 6 shows the lower membrane 54b schematically detail.
  • A the depth of the membrane 54b denotes, 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 that in Figure 1 shown fuel system 10 is used. you recognizes 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 a spring-loaded plate valve formed, which of a plunger (without reference number) the quantity control valve 32 during a delivery stroke of the Forced piston 88 forced into an open position can be.
  • Coaxial with a cylinder center axis 90 is in the outer Limiting surface of the cylinder housing 92 a circumferential Level 94 incorporated. About this is a housing sleeve 96th postponed. By the revolving stage 94 and the Housing sleeve 96 is a to the cylinder center axis 90th circumferential annular space 66 created. This communicates to the one via a channel 100 with a low pressure inlet 102 the fuel pump 18. On the other hand he communicates via a channel 104 having a pressure relief groove 106, which in a cylinder bore 108 in which the piston 88 is guided is, exists.
  • annular space 66 In the annular space 66 are two annular circumferential Membranes 54a and 54b arranged. Their outer edges are via welds 57a to 57d on the one hand with the Cylinder housing 92 and the other with the housing sleeve 96th welded. As a result, two separate Gas volumes created 58a and 58b. Between them is one Fluid region 64 of the working space 66 is present, which in particular via the channel 100 with the low pressure inlet 102 communicates. The annulus 66 and the gas volumes 58a and 58b form in this way a pressure damper 36, which is coaxial with the cylinder center axis 90 of the high-pressure fuel pump 18 is arranged.
  • FIG 8 is a modified embodiment of a such annular pressure damper 36 shown.
  • the pressure damper 36 which is shown in FIG. 8, includes a flattened metal tube 54, which on the Ends gas-tight welded. Its interior forms Gas volume 58.
  • the metal tube 54a is in the working space 66th spiral and helical coaxial with the cylinder center axis 90 wound. This is one thing relative to the housing sleeve 96 and the other to the in Figure 8 upper and lower faces of the working space 66 under a bias and is thereby fixed.
  • FIG. 9 shows a further variant of a pressure damper 36 shown. It applies here and in all subsequent Figures that have such elements and areas which Equivalent functions to elements and areas that already related to previous ones Figures have been explained, the same reference numerals wear. Normally they will not be detailed again explained.
  • the pressure damper 36 shown is in the left half Figure 9 designed differently than on the right half. Both devices 36 have in common that they only over have a single membrane 54. This is in the range its holding portion 72 in FIG. 57 with the upper part 40 of FIG Housing welded. Unlike the example in the FIGS. 2 and 3 have the membrane shown in FIG Membrane 54 a bellows portion 110, which between the bead portion 76 and the holding portion 72 are arranged is composed of individual segments 110a to 110d is. This bellows portion 110 allows a comparatively large volume change of the membrane 54 and the housing 40 trapped gas volume 58th
  • the gas volume 58 is thereby reduced overall, that between the diaphragm 54 and the upper part 40 of the Housing a filler 112 on the upper part 40 of the housing is attached.
  • a filler 112 on the upper part 40 of the housing is attached.
  • the Stopper portion 80 a to the filling body 112 extends. ever after either the filler 112 or the acts Lower part 38 of the housing as a counter surface 80 b for the Stopper portion 80a.
  • the gas volume 58 enclosed by the membrane 54 is filled with helium. This is under an overpressure, which is about half of the maximum in operation occurring overpressure, minus that Pressure increase, which by the compression of the membrane 54 is caused. This is for the membrane 54 a used magnetic metal material. This affects the Pressure damper 36 similar to a "dust catcher", because by they become magnetic debris from the fluid intercepted and their distribution in the fluid system 10th prevented.
  • the individual segments 110a to 110d of the Bellows section 110 in a welding device (not shown) stacked. Then the welding device closed and evacuated their interior. Then the Interior of the welding device filled with helium up to a desired internal pressure.
  • the individual segments 110a to 110d compressed and welded together in 114 for clarity, this reference number is only at one point on the left side of FIG. 9 entered).
  • FIG. 10 shown pressure damper 36 differs from the shown in Figure 9 in that instead of a separate packing 112 in the upper part 40 of the housing Deep-drawn section 112 is present which on the one hand the trapped gas volume 58 reduced and on the other hand has the counter surface 80b, the with the abutment portion 80a of the diaphragm 54 together acts.
  • FIG. 11 again shows an embodiment in which a separate packing 112 is present, which however not hollow, but solid and beyond in a stopper portion 80a of the diaphragm 54 facing region 116 has a smaller diameter having.
  • the contour of the filling body 112 of FIG 11 something adapted to the contour of the diaphragm 54, so that the corresponding gas volume 58 is particularly low.
  • FIG. 12 shows an embodiment in which two diaphragms 54a and 54b are present, respectively
  • the embodiment of a shown in Figure 4 Pressure damper 36 In contrast to Figure 4 is in the in Figure 12 shown embodiment for each membrane 54a and 54b, there is a bellows portion 110 which However, it is simpler than that of FIGS. 9 to 11.
  • the pressure damper shown in FIG has - analogous to that shown in Figures 4 and 5 - upper and lower clamping rings 82 and 84, which, however, in FIG 12 are shown only schematically. Through this, the hydraulically effective surface of the membranes 54a and 54b maximizes, resulting in a reduction of the overall size the pressure damper 36 can be used.
  • the clamping rings 82 and 84 are but spring sections 118 and 120 on Upper part 40 and supported on the lower part 38 of the housing. In this way, manufacturing tolerances of the membranes 54a and 54b.
  • the one central Opening 124 has.
  • the retaining ring 122 is between the two halves 112a and 112b of the packing 112 jammed.
  • the Packing 112 is provided with a circumferential groove in the the edge of the opening 124 of the retaining ring 122 engages.
  • an integral embodiment 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.
  • this pressure damper 36 is no Fillers present, making this device similar to the one constructed as shown in Figs. 4 and 5 is constructed.
  • the differences relate in particular to the clamping rings 82 and 84, with which the membranes 54a and 54b on the housing 40th and 38 are held: the clamping rings 82 and 84 face projecting spring portions, wherein a spring portion 118a and 120a, the membranes 54a and 54b in Figure 13 in positioned in the vertical direction, whereas a Spring section 118b and 120b, the two membranes 54 and 56 positioned in Figure 13 in the horizontal direction or centered.
  • the spring sections 118a and 120a are separated by individual radially inwardly facing bracket of the two clamping rings 82nd and 84 formed in the one shown in FIG Mounting position against the upper part 40 and the lower part 38 of the Housing are biased.
  • the spring sections 118b or In turn, 120b are separated by radially outward acting strap formed on the inner surface of the upper part 40 of the housing 40 bear or against them are biased.
  • FIG. 14 is a modified again Embodiment of a pressure damper 36 shown. at this is at the radially outer edge of the bead portion 76th a tubular attachment portion 122 is provided which is approximately parallel to the central axis 41 of the Pressure damper 36 extends and in 57 with its edge the housing 40 is welded. Ultimately, then is the Membrane 54 attached directly to the housing 40, what else spares required additional constructions. additionally
  • the pressure damper 36 in FIG. 14 has a clamping ring 124 on which the fastening portion 122 from radially inward forth against the housing 40 presses. This will be the Weld 57 mechanically relieved.
  • the radial maximum external weld 57 allows the use of the total inner diameter of the housing 40 as a hydraulic effective diameter. This lowers the manufacturing costs.
  • the gas volume 58 can either in the manufacture of the Weld 57 can be set up (welding in one Pressure chamber). Or the work space 66 is retroactive filled through the opening 60, which then through the element 62 is closed. The latter can, for example, with the Housing 40 are welded. As with the Embodiments of Figures 9 to 11 is also in the shown in Figure 14 the 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.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pipe Accessories (AREA)
  • Fuel-Injection Apparatus (AREA)
EP03015623A 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 EP1411236B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP10180722A 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
EP10180727A 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 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

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE10248822 2002-10-19
DE10248822 2002-10-19
DE10327408.1A DE10327408B4 (de) 2002-10-19 2003-06-18 Vorrichtung zum Dämpfen von Druckpulsationen in einem Kraftstoffsystem einer Brennkraftmaschine
DE10327408 2003-06-18

Related Child Applications (6)

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EP10180722A Division-Into 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
EP10180722A Division 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
EP10180742.8A Division-Into 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
EP10180742.8A Division 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
EP10180727A Division-Into 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
EP10180727A Division 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

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EP1617072A3 (fr) * 2004-07-17 2006-05-17 Robert Bosch Gmbh Système d'injection de carburant pour moteur à combustion interne
WO2007144229A1 (fr) * 2006-06-16 2007-12-21 Robert Bosch Gmbh Injecteur de carburant
CH698080B1 (de) * 2004-08-04 2009-05-15 Luca Frediani Pulsationsdämpfer.
EP1995446A3 (fr) * 2007-05-21 2009-10-07 Hitachi Ltd. Amortisseur de pulsations de pression et pompe de carburant à haute pression avec amortisseur de pulsations de pression
EP2112368A3 (fr) * 2008-04-25 2009-11-11 Hitachi Ltd. Mécanisme de retenue de pulsation de pression de carburant et pompe à carburant à haute pression de moteur à combustion interne avec ce mécanisme
ITBO20090720A1 (it) * 2009-11-03 2011-05-04 Magneti Marelli Spa Pompa carburante con dispositivo smorzatore perfezionato per un sistema di iniezione diretta
GB2481682A (en) * 2010-06-29 2012-01-04 Bosch Gmbh Robert A pulsation damper element for a fluid pump
EP2410167A1 (fr) * 2009-03-17 2012-01-25 Toyota Jidosha Kabushiki Kaisha Amortisseur de pulsation
JP2012197732A (ja) * 2011-03-22 2012-10-18 Denso Corp パルセーションダンパおよびこれを備えた高圧ポンプ
WO2015039955A1 (fr) * 2013-09-19 2015-03-26 Robert Bosch Gmbh Système de transport de fluide
EP2244917B1 (fr) * 2008-02-18 2015-12-02 Continental Teves AG & Co. oHG Capsule d amortissement des pulsations
DE102014219997A1 (de) 2014-10-02 2016-04-07 Robert Bosch Gmbh Membrandose zum Dämpfen von Druckpulsationen in einem Niederdruckbereich einer Kolbenpumpe
WO2016170053A1 (fr) * 2015-04-22 2016-10-27 Eagle Simrax B.V. Système d'injection de carburant et amortisseur utilisé dans le système d'injection de carburant
EP3130803A1 (fr) * 2015-08-13 2017-02-15 Mahle International GmbH Dispositif de pompage, en particulier pompe a pistons axiaux pour un dispositif de recuperation de la chaleur perdue d'un vehicule automobile
DE102015219537A1 (de) 2015-10-08 2017-04-27 Robert Bosch Gmbh Membrandose zum Dämpfen von Druckpulsationen in einem Niederdruckbereich einer Kolbenpumpe
WO2017157554A1 (fr) * 2016-03-14 2017-09-21 Robert Bosch Gmbh Pompe haute pression comprenant un amortisseur de fluide
EP3438510A4 (fr) * 2016-03-28 2019-11-06 Eagle Industry Co., Ltd. Amortisseur à membrane métallique
CN110617162A (zh) * 2018-06-20 2019-12-27 罗伯特·博世有限公司 用于内燃机的冷却系统
EP3715617A4 (fr) * 2017-11-24 2021-07-14 Eagle Industry Co., Ltd. Amortisseur à diaphragme métallique et procédé de fabrication associé
IT202000017773A1 (it) 2020-07-22 2022-01-22 Marelli Europe Spa Pompa carburante con dispositivo smorzatore perfezionato per un sistema di iniezione diretta

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JP5445441B2 (ja) * 2010-12-23 2014-03-19 株式会社デンソー 高圧ポンプ
JP5682335B2 (ja) * 2011-01-28 2015-03-11 株式会社デンソー 高圧ポンプ
CN102619660B (zh) 2011-01-28 2015-06-24 株式会社电装 高压泵
JP2012184757A (ja) * 2011-03-08 2012-09-27 Denso Corp ダンパ装置およびこれを備えた高圧ポンプ
JP5382551B2 (ja) 2011-03-31 2014-01-08 株式会社デンソー 高圧ポンプ
JP5628121B2 (ja) 2011-09-20 2014-11-19 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
JP5821769B2 (ja) 2012-04-24 2015-11-24 株式会社デンソー ダンパ装置
JP5979606B2 (ja) 2012-10-04 2016-08-24 イーグル工業株式会社 ダイアフラムダンパ
DE102013219428A1 (de) 2013-09-26 2015-03-26 Continental Automotive Gmbh Dämpfer für eine Hochdruckpumpe
JP2015017619A (ja) * 2014-10-27 2015-01-29 株式会社デンソー 高圧ポンプ
JP5892397B2 (ja) * 2014-10-30 2016-03-23 株式会社デンソー パルセーションダンパ
JP6432441B2 (ja) * 2014-11-20 2018-12-05 株式会社デンソー 高圧ポンプ
JP6527689B2 (ja) * 2014-12-12 2019-06-05 株式会社不二工機 ダイヤフラム及びそれを用いたパルセーションダンパ
JP6012785B2 (ja) * 2015-01-30 2016-10-25 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
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
DE102016201082B4 (de) * 2016-01-26 2017-10-05 Continental Automotive Gmbh Kraftstoffhochdruckpumpe
JP6111358B2 (ja) * 2016-03-28 2017-04-05 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
JP6569589B2 (ja) 2016-04-28 2019-09-04 株式会社デンソー 高圧ポンプ
WO2017195415A1 (fr) * 2016-05-13 2017-11-16 日立オートモティブシステムズ株式会社 Dispositif de réduction de pulsation de pression et élément d'amortissement de pulsation pour système de pression hydraulique
DE102016212458A1 (de) * 2016-07-08 2018-01-11 Robert Bosch Gmbh Kraftstoffhochdruckpumpe
JP6310026B2 (ja) * 2016-09-20 2018-04-11 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
JP6888408B2 (ja) * 2017-05-11 2021-06-16 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
JP6511559B2 (ja) * 2018-03-13 2019-05-15 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
KR20200140902A (ko) 2018-05-25 2020-12-16 이구루코교 가부시기가이샤 댐퍼 장치
JP2019105273A (ja) * 2019-04-05 2019-06-27 日立オートモティブシステムズ株式会社 燃料の圧力脈動低減機構、及びそれを備えた内燃機関の高圧燃料供給ポンプ
DE102019212005A1 (de) * 2019-08-09 2021-02-11 Robert Bosch Gmbh Kraftstoff-Hochdruckpumpe
WO2021095555A1 (fr) * 2019-11-15 2021-05-20 日立Astemo株式会社 Diaphragme métallique, amortisseur métallique et pompe à carburant

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JPS6467299A (en) 1987-09-07 1989-03-13 Daiki Nakayama Removing method for heavy metal from waste mud
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Cited By (37)

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Publication number Priority date Publication date Assignee Title
EP1617072A3 (fr) * 2004-07-17 2006-05-17 Robert Bosch Gmbh Système d'injection de carburant pour moteur à combustion interne
CH698080B1 (de) * 2004-08-04 2009-05-15 Luca Frediani Pulsationsdämpfer.
US8038083B2 (en) 2006-06-16 2011-10-18 Robert Bosch Gmbh Fuel injector
WO2007144229A1 (fr) * 2006-06-16 2007-12-21 Robert Bosch Gmbh Injecteur de carburant
EP1995446A3 (fr) * 2007-05-21 2009-10-07 Hitachi Ltd. Amortisseur de pulsations de pression et pompe de carburant à haute pression avec amortisseur de pulsations de pression
US8366421B2 (en) 2007-05-21 2013-02-05 Hitachi, Ltd. Fluid pressure pulsation damper mechanism and high-pressure fuel pump equipped with fluid pressure pulsation damper mechanism
EP2244917B1 (fr) * 2008-02-18 2015-12-02 Continental Teves AG & Co. oHG Capsule d amortissement des pulsations
US8876502B2 (en) 2008-04-25 2014-11-04 Hitachi, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
US10107285B2 (en) 2008-04-25 2018-10-23 Hitachi Automotive Systems, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
US11047380B2 (en) 2008-04-25 2021-06-29 Hitachi Automotive Systems, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
US9709055B2 (en) 2008-04-25 2017-07-18 Hitachi Automotive Systems, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
EP2112368A3 (fr) * 2008-04-25 2009-11-11 Hitachi Ltd. Mécanisme de retenue de pulsation de pression de carburant et pompe à carburant à haute pression de moteur à combustion interne avec ce mécanisme
EP2466114A1 (fr) * 2008-04-25 2012-06-20 Hitachi Ltd. Pompe à carburant à haute pression de moteur à combustion interne avec un mécanisme de réduction de pulsation de pression de carburant
US20090288639A1 (en) * 2008-04-25 2009-11-26 Hitachi, Ltd. Mechanism for Restraining Fuel Pressure Pulsation and High Pessure Fuel Supply Pump of Internal Combustion Engine with Such Mechanism
US8393881B2 (en) 2008-04-25 2013-03-12 Hitachi, Ltd. Mechanism for restraining fuel pressure pulsation and high pressure fuel supply pump of internal combustion engine with such mechanism
US9057348B2 (en) 2009-03-17 2015-06-16 Toyota Jidosha Kabushiki Kaisha Pulsation damper
EP2410167A4 (fr) * 2009-03-17 2012-09-05 Toyota Motor Co Ltd Amortisseur de pulsation
EP2410167A1 (fr) * 2009-03-17 2012-01-25 Toyota Jidosha Kabushiki Kaisha Amortisseur de pulsation
ITBO20090720A1 (it) * 2009-11-03 2011-05-04 Magneti Marelli Spa Pompa carburante con dispositivo smorzatore perfezionato per un sistema di iniezione diretta
CN102052220B (zh) * 2009-11-03 2014-11-12 马涅蒂-马瑞利公司 用于直接喷射系统的具有改进的阻尼装置的燃料泵
CN102052220A (zh) * 2009-11-03 2011-05-11 马涅蒂-马瑞利公司 用于直接喷射系统的具有改进的阻尼装置的燃料泵
EP2317119A1 (fr) * 2009-11-03 2011-05-04 Magneti Marelli S.p.A. Pompe à combustible dotée d'un dispositif d'amortissement pour un système à injection directe
GB2481682B (en) * 2010-06-29 2012-10-24 Bosch Gmbh Robert Pulsation damper element for a fluid pump and associated fluid pump
GB2481682A (en) * 2010-06-29 2012-01-04 Bosch Gmbh Robert A pulsation damper element for a fluid pump
JP2012197732A (ja) * 2011-03-22 2012-10-18 Denso Corp パルセーションダンパおよびこれを備えた高圧ポンプ
WO2015039955A1 (fr) * 2013-09-19 2015-03-26 Robert Bosch Gmbh Système de transport de fluide
DE102014219997A1 (de) 2014-10-02 2016-04-07 Robert Bosch Gmbh Membrandose zum Dämpfen von Druckpulsationen in einem Niederdruckbereich einer Kolbenpumpe
WO2016170053A1 (fr) * 2015-04-22 2016-10-27 Eagle Simrax B.V. Système d'injection de carburant et amortisseur utilisé dans le système d'injection de carburant
EP3130803A1 (fr) * 2015-08-13 2017-02-15 Mahle International GmbH Dispositif de pompage, en particulier pompe a pistons axiaux pour un dispositif de recuperation de la chaleur perdue d'un vehicule automobile
US10662931B2 (en) 2015-10-08 2020-05-26 Robert Bosch Gmbh Diaphragm cell for damping pressure pulsations in a low-pressure region of a piston pump
DE102015219537A1 (de) 2015-10-08 2017-04-27 Robert Bosch Gmbh Membrandose zum Dämpfen von Druckpulsationen in einem Niederdruckbereich einer Kolbenpumpe
WO2017157554A1 (fr) * 2016-03-14 2017-09-21 Robert Bosch Gmbh Pompe haute pression comprenant un amortisseur de fluide
EP3438510A4 (fr) * 2016-03-28 2019-11-06 Eagle Industry Co., Ltd. Amortisseur à membrane métallique
EP3715617A4 (fr) * 2017-11-24 2021-07-14 Eagle Industry Co., Ltd. Amortisseur à diaphragme métallique et procédé de fabrication associé
US11181220B2 (en) 2017-11-24 2021-11-23 Eagle Industry Co., Ltd. Metal diaphragm damper and manufacturing method for the same
CN110617162A (zh) * 2018-06-20 2019-12-27 罗伯特·博世有限公司 用于内燃机的冷却系统
IT202000017773A1 (it) 2020-07-22 2022-01-22 Marelli Europe Spa Pompa carburante con dispositivo smorzatore perfezionato per un sistema di iniezione diretta

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EP1411236B1 (fr) 2012-10-10
JP4478431B2 (ja) 2010-06-09
EP1411236A3 (fr) 2007-04-11
JP2004138071A (ja) 2004-05-13

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