EP1411236A2 - Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine - Google Patents
Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine Download PDFInfo
- 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
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Classifications
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- 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
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- 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
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- 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
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- 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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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- General Engineering & Computer Science (AREA)
- Pipe Accessories (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
- Figur 1
- eine schematische Darstellung eines Kraftstoffsystems einer Brennkraftmaschine mit einer Kraftstoffpumpe und einer dort vorhandenen Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 2
- einen Schnitt durch ein erstes Ausführungsbeispiel der Vorrichtung zum Dämpfen von Druckpulsationen von Figur 1;
- Figur 3
- ein Detail III der Vorrichtung zum Dämpfen von Druckpulsationen von Figur 2;
- Figur 4
- einen Schnitt durch ein zweites Ausführungsbeispiel der Vorrichtung zum Dämpfen von Druckpulsationen von Figur 1;
- Figur 5
- ein Detail V der Vorrichtung zum Dämpfen von Druckpulsationen von Figur 4;
- Figur 6
- einen schematischen Schnitt durch eine Membran der Vorrichtung zum Dämpfen von Druckpulsationen von Figur 4;
- Figur 7
- einen Schnitt durch eine Kraftstoffpumpe mit einem dritten Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 8
- einen Schnitt durch einen Bereich der Kraftstoffpumpe von Figur 7 mit einem vierten Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 9
- einen Schnitt durch ein fünftes und ein sechstes Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 10
- einen Schnitt durch ein siebtes Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 11
- einen Schnitt durch ein achtes Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 12
- einen Schnitt durch ein neuntes Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen;
- Figur 13
- einen Schnitt durch ein zehntes Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen; und
- Figur 14
- einen Teilschnitt durch ein elftes und ein zwölftes Ausführungsbeispiel einer Vorrichtung zum Dämpfen von Druckpulsationen.
Claims (33)
- Vorrichtung (36) zum Dämpfen von Druckpulsationen in einem Fluidsystem (16), insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine, mit einem Gehäuse (38, 40) und mit mindestens einem Arbeitsraum (66), welcher wenigstens bereichsweise mit dem Fluidsystem (16) kommuniziert, dadurch gekennzeichnet, dass innerhalb des Arbeitsraums (66) mindestens ein durch eine Membran (54) dicht abgeschlossenes Gasvolumen (58) vorhanden ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (54) aus Metall ist.
- Vorrichtung (36) nach Anspruch 2, dadurch gekennzeichnet, dass die Membran durch ein dünnwandiges und an seinen Enden gasdicht verschlossenes Metallrohr (54) begrenzt wird.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass mindestens eine Außenwand des Arbeitsraums ebenfalls als Membran ausgebildet ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das eingeschlossene Gasvolumen (58) bei einem Norm-Außendruck einen definierten Druck aufweist, vorzugsweise einen Überdruck.
- Vorrichtung (36) nach Anspruch 5, dadurch gekennzeichnet, dass das Gasvolumen (58) eine verschließbare Öffnung (60) aufweist, über die der Druck eingestellt werden kann.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (54) mindestens eine Sicke (78) aufweist.
- Vorrichtung (36) nach Anspruch 7, dadurch gekennzeichnet, dass die Membran (54) mehrere Sicken (78) aufweist, welche unterschiedliche Höhe und/oder einen unterschiedlichen Verlauf und/oder einen unterschiedlichen Querschnitt haben.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (54a) mindestens einen Anschlagabschnitt (80a) aufweist, welcher bei einer maximalen Auslenkung der Membran (54) mit einer Gegenfläche (80b) in Anlage kommt.
- Vorrichtung (36) nach Anspruch 9, dadurch gekennzeichnet, dass die Gegenfläche (80b) an dem Gehäuse (40), an einem separaten Anschlagteil (112), und/oder an einer weiteren Membran (54b) ausgebildet ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das eingeschlossene Gasvolumen (58) durch einen Füllbereich (112) reduziert wird.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Gasvolumen (58) durch mindestens zwei Membranen (54a, 54b) begrenzt wird, die im Bereich ihrer Ränder eingespannt sind (82, 84).
- Vorrichtung (36) nach Anspruch 12, dadurch gekennzeichnet, dass die Membranen (54a, 54b) insgesamt im Wesentlichen parallel sind.
- Vorrichtung (36) nach Anspruch 13 in Verbindung mit Anspruch 10, dadurch gekennzeichnet, dass das Gasvolumen (58) zwischen den beiden Membranen (54a, 54b) gebildet ist und die beiden Membranen (54a, 54b) jeweils mindestens eine Anschlagfläche (80a) bzw. eine Gegenfläche (80b) aufweisen, welche sich bei einer maximalen Auslenkung der beiden Membranen (54a, 54b) berühren.
- Vorrichtung (36) nach einem der Ansprüche 12 bis 14, dadurch gekennzeichnet, dass die Ränder der beiden Membranen (54a, 54b) miteinander dicht verbunden und radial einwärts von der Abdichtlinie (57) eingespannt sind (82, 84).
- Vorrichtung (36) nach Anspruch 15, dadurch gekennzeichnet, dass die Einspannung (82, 84) über eine konstruktive Elastizität (118, 120) verfügt.
- Vorrichtung (36) nach einem der Ansprüche 12 bis 16, dadurch gekennzeichnet, dass die beiden Membranen (54a, 54b) identisch sind.
- Vorrichtung (36) nach einem der Ansprüche 12 bis 17, dadurch gekennzeichnet, dass der Arbeitsraum (66) durch die beiden Membranen (54a, 54b) in zwei Bereiche (64, 68) unterteilt wird, welche durch eine Fluidverbindung (70) miteinander kommunizieren.
- Vorrichtung (36) nach einem der Ansprüche 12 bis 18, dadurch gekennzeichnet, dass zwischen den beiden Membranen (54a, 54b) ein ringförmiger Abstandshalter (46) vorhanden ist.
- Vorrichtung (36) nach den Ansprüchen 17 und 19, dadurch gekennzeichnet, dass die Fluidverbindung (70) in dem Abstandshalter ausgebildet ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie in ein Gehäuse (92) einer Kraftstoffpumpe (18) integriert ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Arbeitsraum einen Ringraum (66) umfasst und das Gasvolumen (58) ringförmig ist.
- Vorrichtung (36) nach den Ansprüchen 20 und 21, dadurch gekennzeichnet, dass der Arbeitsraum (66) und das Gasvolumen (58) in oder an einem Zylinder (92) einer Kraftstoffpumpe (18) wenigstens in etwa koaxial zur Zylinderachse (90) angeordnet sind.
- Vorrichtung (36) nach einem der Ansprüche 21 oder 22, dadurch gekennzeichnet, dass das Gasvolumen (58) in der Art einer Spirale innerhalb des Ringraums (66) angeordnet ist, wobei die Spirale (58) und der Ringraum (66) wenigstens in etwa koaxial sind.
- Vorrichtung (36) nach Anspruch 23, dadurch gekennzeichnet, dass das spiralförmige Gasvolumen (58) gegen die Außenwand des Arbeitsraums (66) vorgespannt ist.
- Vorrichtung (36) nach einem der Ansprüche 23 oder 24, dadurch gekennzeichnet, dass das spiralförmige Gasvolumen (58) schraubenförmig in axialer Richtung des Arbeitsraums (66) verläuft.
- Vorrichtung (36) nach Anspruch 25, dadurch gekennzeichnet, dass das spiral- und schraubenförmige Gasvolumen (58) in axialer Richtung gegen die Stirnenden des Arbeitsraums (66) vorgespannt ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Gasvolumen (58) mit Helium gefüllt ist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (54) und/oder das Gehäuse wenigstens bereichsweise magnetisch sind.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (36) wenigstens zum Teil aus einem Bandmaterial hergestellt ist, welches Eigenspannungen aufweist.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (54) mindestens einen Sickenabschnitt (76) und mindestens einen Faltenbalgabschnitt (110) umfasst.
- Vorrichtung (36) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Membran (54) an ihrem radial äußeren Rand einen Befestigungsabschnitt (122) aufweist, welcher sich in etwa parallel zur Mittelachse (41) erstreckt und an dem Gehäuse (40) befestigt ist.
- Vorrichtung (36) nach Anspruch 32, dadurch gekennzeichnet, dass sie eine Spanneinrichtung (124) umfasst, welche den Befestigungsabschnitt (122) radial gegen das Gehäuse (40) beaufschlagt.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10180742.8A EP2278151B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180722A EP2278150B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180727A EP2284384B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
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)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10180722A Division-Into EP2278150B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180722A Division EP2278150B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180727A Division-Into EP2284384B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180727A Division EP2284384B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180742.8A Division EP2278151B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
EP10180742.8A Division-Into EP2278151B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1411236A2 true EP1411236A2 (de) | 2004-04-21 |
EP1411236A3 EP1411236A3 (de) | 2007-04-11 |
EP1411236B1 EP1411236B1 (de) | 2012-10-10 |
Family
ID=32043977
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03015623A Expired - Lifetime EP1411236B1 (de) | 2002-10-19 | 2003-07-16 | Vorrichtung zum Dämpfen von Druckpulsationen in einem Fluidsystem, insbesondere in einem Kraftstoffsystem einer Brennkraftmaschine |
Country Status (2)
Country | Link |
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EP (1) | EP1411236B1 (de) |
JP (1) | JP4478431B2 (de) |
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EP1617072A3 (de) * | 2004-07-17 | 2006-05-17 | Robert Bosch Gmbh | Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine |
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 (de) * | 2006-06-16 | 2007-12-21 | Robert Bosch Gmbh | Kraftstoffinjektor |
EP1995446A3 (de) * | 2007-05-21 | 2009-10-07 | Hitachi Ltd. | Druckpulsationsdämpfer und Hochdruckkraftstoffpumpe mit Druckpulsationsdämpfer |
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 (de) * | 2008-02-18 | 2015-12-02 | Continental Teves AG & Co. oHG | Pulsationsdämpfungskapsel |
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 |
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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 |
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EP3438510A4 (de) * | 2016-03-28 | 2019-11-06 | Eagle Industry Co., Ltd. | Metallmembrandämpfer |
EP3715617A4 (de) * | 2017-11-24 | 2021-07-14 | Eagle Industry Co., Ltd. | Metallmembrandämpfer und verfahren zu seiner herstellung |
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 |
Also Published As
Publication number | Publication date |
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JP4478431B2 (ja) | 2010-06-09 |
EP1411236B1 (de) | 2012-10-10 |
EP1411236A3 (de) | 2007-04-11 |
JP2004138071A (ja) | 2004-05-13 |
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