EP2989316B1 - Piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine - Google Patents
Piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine Download PDFInfo
- Publication number
- EP2989316B1 EP2989316B1 EP14713093.4A EP14713093A EP2989316B1 EP 2989316 B1 EP2989316 B1 EP 2989316B1 EP 14713093 A EP14713093 A EP 14713093A EP 2989316 B1 EP2989316 B1 EP 2989316B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston pump
- radially
- piston
- shell
- outer 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.)
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Links
- 239000000446 fuel Substances 0.000 title claims description 31
- 238000002485 combustion reaction Methods 0.000 title claims description 9
- 238000003754 machining Methods 0.000 claims description 7
- 239000002184 metal Substances 0.000 claims description 5
- 239000012530 fluid Substances 0.000 claims description 4
- 238000001746 injection moulding Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 4
- 238000005495 investment casting Methods 0.000 claims description 3
- 239000000843 powder Substances 0.000 claims description 3
- 239000000463 material Substances 0.000 description 8
- 238000004519 manufacturing process Methods 0.000 description 6
- 239000007787 solid Substances 0.000 description 3
- 206010010904 Convulsion Diseases 0.000 description 2
- 238000005520 cutting process Methods 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 230000010349 pulsation Effects 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 240000001439 Opuntia Species 0.000 description 1
- 235000004727 Opuntia ficus indica Nutrition 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 238000005242 forging Methods 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 239000002994 raw material Substances 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000011343 solid material Substances 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
Images
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
- F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
- F02M39/02—Arrangements of fuel-injection apparatus to facilitate the driving of pumps; Arrangements of fuel-injection pumps; Pump drives
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/48—Assembling; Disassembling; Replacing
-
- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8046—Fuel injection apparatus manufacture, repair or assembly the manufacture involving injection moulding, e.g. of plastic or metal
-
- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8053—Fuel injection apparatus manufacture, repair or assembly involving mechanical deformation of the apparatus or parts thereof
-
- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit
-
- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8069—Fuel injection apparatus manufacture, repair or assembly involving removal of material from the fuel apparatus, e.g. by punching, hydro-erosion or mechanical operation
-
- 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
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8084—Fuel injection apparatus manufacture, repair or assembly involving welding or soldering
Definitions
- the invention relates to a piston pump according to the preamble of claim 1.
- the invention has the advantage that a weight of a fuel high-pressure pump designed as a piston pump can be reduced, and material costs and production costs can be reduced. In particular, a quantity of material in such areas of the piston pump can be reduced, which are of little importance for the function of the piston pump and less critical for the strength.
- Massively designed elements of the piston pump for example an inner housing core, are preferably used (only) in a high-pressure region of the piston pump. Accordingly, comparatively thin-walled elements can be used in a low-pressure region of the piston pump. At the same time, this can result in functional advantages in the operation of the piston pump.
- the number of elements of the piston pump can be reduced, wherein a mounting flange and a lid of the piston pump are integrated into an outer housing shell. This can preferably be done in one piece.
- the piston pump according to the invention has comparatively large space sections which are filled with fuel during operation. This makes it possible that elements or fluid areas within the piston pump can be better hydraulically connected to each other. For example, this relates to a so-called "damper space” and a "step space” of the piston pump and a hydraulic connection to a quantity control valve. This can result in lower suction losses of the piston pump and a better filling of a working space of the piston pump. As a result, a vapor formation can be reduced within the piston pump, which may result in a lower risk of seizure.
- a pre-pressure of the piston pump according to the invention can be lowered.
- the piston pump or the outer housing jacket encloses a comparatively large volume of fuel, whereby hydraulic pulsations in the low-pressure region of the piston pump can be better damped.
- the piston pump according to the invention can be manufactured with a lower cost of machining.
- Elements of the piston pump - in particular in the low-pressure region - can be designed as relatively simply produced turned parts or as sheet-metal deep-drawn parts. This is also possible according to the invention for a so-called "customer connection", by means of which the piston pump can be mounted, for example, in a mounting structure of an internal combustion engine.
- the invention relates to a piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine, with an inner housing core to which a cylinder liner is attached (which includes that the inner housing core forms the cylinder liner), and with an outer housing shell, which at least partially the inner Housing core surrounded by radially outside.
- at least one radially projecting edge section of the outer housing shell forms at least one part of a fastening flange with which the piston pump can be fastened to a mounting structure.
- the outer housing shell and at least a part of the mounting flange are designed as a common part.
- the inner housing core can be made from a blank which requires only about one fourth of the amount of material of a comparable conventional element.
- the radially projecting edge portion is pressed a separate part and with a jacket portion of the housing shell and / or welded.
- the housing jacket has a holding section which radially inwardly supports a piston seal and / or radially outwardly an O-ring seal and / or axially outside a piston spring.
- the outer housing shell can be used in a simple manner for attachment of further elements of the piston pump, so that corresponding separate holders can be omitted.
- the piston radially outwardly surrounding piston seal can seal a working space of the piston pump to the outside.
- the O-ring seal makes it possible to seal the piston pump as a whole against the mounting structure or an opening of the mounting structure, in which the piston pump is inserted to the outside.
- the piston spring counteracts a force of an acting on an end portion of the piston cam. As a result, the piston pump according to the invention is simplified and cheaper overall.
- the support portion is a separate part and welded to a shell portion of the housing shell axially or radially and / or compressed axially or radially with this.
- this makes it possible to carry out the mounting portion with a different material thickness.
- the support portion is specifically adapted to its respective function, whereby the piston pump improved overall and weight and material and ultimately costs are saved.
- the outer housing shell is at least partially made by means of plastic deformation, in particular by deep drawing.
- the housing shell can be produced in a particularly simple and cost-effective manner.
- the inner housing core is at least partially substantially cylindrical or designed as a flat bar, wherein an axis of the cylinder or flat bar is arranged perpendicular to a longitudinal axis of the piston pump.
- the inner housing core is designed substantially as a solid component, which is brought by means of cutting reworking in a desired shape.
- an inlet valve and an outlet valve of the piston pump according to the invention are arranged on the end faces of the cylinder or flat bar.
- a cylinder liner of the piston pump in the said cylinder or flat bar can be at least partially arranged.
- the cylinder liner is arranged, for example, perpendicular to the axis of the cylinder or flat bar. Due to the - preferably - solid design of the cylinder or flat bar this is particularly well suited for high fuel pressures.
- the cylindrical shape itself may have advantages for the assembly of the inlet valve and the outlet valve.
- the piston pump of the inner housing core is designed substantially as a cylindrical disc, wherein an axis of the cylindrical disc is arranged parallel or even coaxial with a longitudinal axis of the piston pump.
- this makes it possible that hydraulic connections of the piston pump can be arranged in an angle defined to a longitudinal axis of the piston pump.
- the angle can be structurally chosen comparatively arbitrary.
- the thus formed inner housing core can be particularly easily and permanently disposed on radially inner portions of the outer housing shell or connected thereto. As a result, the robustness of the piston pump according to the invention can be improved.
- the inner housing core is carried out by means of machining.
- the inner housing core so to speak, represents a central element of the piston pump according to the invention.
- the inner housing core can therefore be designed specifically, whereby the connection to other elements of the piston pump can be improved.
- the manufacture of the piston pump can be made cheaper if the inner casing core is made by a method of metal injection molding (MIM) or by precision casting. Thereby, the number of steps for the production of the inner housing core can be reduced, which can result in cost advantages.
- MIM metal injection molding
- a jacket section of the outer housing jacket is designed substantially as a radially symmetrical polygon in a plane perpendicular to a longitudinal axis of the piston pump.
- the outer housing shell sections partially planar surfaces, on which hydraulic connections of the piston pump can be particularly well arranged.
- the polygon is a hexagon.
- FIG. 1 shows a fuel system 10 for a further not shown internal combustion engine in a much simplified representation.
- a fuel tank 12 fuel via a suction line 14 by means of a feed pump 16 via a low pressure line 18 and via an actuatable by an electromagnetic actuator 20 ("solenoid") quantity control valve 22 a high-pressure fuel pump - hereinafter referred to as piston pump 24 - fed.
- the piston pump 24 is connected via a high-pressure line 26 to a high-pressure accumulator 28 ("common rail").
- FIG. 1 shown schematically.
- Other elements, such as valves of the piston pump 24, are in the FIG. 1 not drawn.
- the electromagnetic actuator 20 is controlled by a control and / or regulating device 42.
- the quantity control valve 22 may also be formed as a unit with the piston pump 24, as in the following FIGS. 2 to 5 will be shown.
- the quantity control valve 22 may be a forcibly openable inlet valve of the piston pump 24.
- the prefeed pump 16 delivers fuel from the fuel tank 12 into the low pressure line 18.
- the mass control valve 22 may be closed and opened in response to a respective demand for fuel. As a result, the amount of fuel delivered into the high-pressure accumulator 28 is influenced.
- the fuel is for example gasoline or diesel fuel.
- FIG. 2 shows a first embodiment of the piston pump 24 for the fuel system 10 of FIG. 1 in longitudinal section.
- the piston pump 24 is arranged at least partially rotationally symmetrical about a vertical longitudinal axis 44 in the drawing.
- the piston pump 24 has an inner solid housing core 46, which is embodied substantially cylindrically around a longitudinal axis 48 arranged perpendicular to the longitudinal axis 44.
- the piston pump 24 has a substantially cup-shaped thin-walled outer housing shell 50 which, among other things, encloses the inner housing core 46 from radially outside.
- the inner housing core 46 of the piston pump 24 according to FIG. 2 is made of a solid material by machining and hydraulically sealed to a radially inner portion of the outer housing shell 50.
- the inner housing core 46 and the outer housing shell 50 together form a housing (not numbered), on which further elements and / or housing parts of the piston pump 24 are arranged, as will be explained below.
- the inner housing core 46 and the outer housing shell 50 are pressed together and / or welded together.
- An underside edge portion 52 of the outer casing shell 50 which is lower in the drawing, is bent slightly in a wave-like manner radially outward.
- the radially projecting edge portion 52 of the outer housing shell 50 at two diametrically opposite locations at the same time a part of a mounting flange 74, with which the piston pump 24 (not shown) can be attached to a mounting structure.
- the mounting structure is for example a cylinder head of the internal combustion engine.
- an inlet pipe 54 is arranged on the outer housing shell 50 and fluid-tightly connected to the outer housing shell 50.
- the inlet pipe 54 is executed or arranged rotationally symmetrical to the longitudinal axis 44 of the piston pump 24.
- a pressure damper 56 in this case a diaphragm pressure damper.
- the inner housing core 46 has coaxially with the longitudinal axis 48 in each case a first stepped bore (without reference numeral) or a second stepped bore (without reference numeral), both of which open into a longitudinal bore 44 coaxial blind bore (without reference numeral), in which the cylinder liner 32 is pressed ,
- a portion of an outlet nozzle 60 is arranged, in which an outlet valve is integrated.
- a portion of the quantity control valve 22 is arranged in the second bore (in the drawing on the right) a portion of the quantity control valve 22 is arranged.
- the outlet port 60 is connected to the high pressure line 26 (see FIG. 1 ) hydraulically connected.
- the quantity control valve 22 and the outlet port 60 are pressed against the inner housing core 46 and in the described holes and welded thereto.
- the cylinder liner 32 has radial openings 32a and 32b, respectively, which hydraulically connect the working space 25 formed in the cylinder liner 32 to the outlet nozzle 60 and to an outlet of the quantity control valve 22, respectively.
- damper chamber 62 Fluid chamber
- a in the drawing below the inner housing core 46 existing space portion forms a so-called stepped space 63.
- the inner housing core 46 has in a volume control valve 22 facing axial end portion radial bores 57 a and 57 b, which an inlet of the quantity control valve 22 with the damper chamber 62 and Hydraulically connect the step room 63.
- a multi-part support portion 65 is arranged.
- the multi-part support portion 65 herein comprises a first support portion formed as a seal support 64, a second support portion configured as a seal retainer 66, and an inner support portion 68.
- the seal support 64, the seal retainer 66, and the inner support portion 68 are each also relative to the longitudinal axis 44 in FIG Essentially rotationally symmetrical.
- the multi-part support portion 65 is part of a "customer connection" by means of which the piston pump 24 can be accommodated in the above-mentioned mounting structure.
- the seal carrier 64, the seal holder 66, and the inner holder portion 68 are manufactured by using stamped bent sheets (deep-drawn parts). Because these elements define the step space 63, which has a comparatively low hydraulic pressure, these elements are comparatively thin and light in design. The three said elements touch each other at least in pairs or at least partially and in pairs positively or materially connected to each other.
- the seal holder 66 is designed in a radially inner region as an annular disc, wherein portions of the seal carrier 64 and the inner support portion 68 protrude through a centrally disposed in the seal holder 66 hole.
- a housing seal 70 which is designed here as an O-ring seal arranged.
- the circumferential shape of the seal carrier 64 together with a radially outer edge portion of the seal holder 66 forms a radially encircling groove, in which the housing seal 70 is held in a form-fitting manner.
- the seal carrier 64 is provided with a in the FIG. 2 bottom end portion of the outer housing shell 50 fluid-tightly connected, welded here.
- FIG. 2 In a lower area of FIG. 2 is concentric with the longitudinal axis 44 arranged as a helical spring piston spring 72 is arranged.
- an upper end portion of the piston spring 72 in the drawing lies axially against a radially extending collar-like portion of the seal holder 66, which thus also forms an axial counter bearing for the piston spring 72.
- An in the drawing lower end portion of the piston spring 72 is axially against a spring plate 73, which is connected to a lower end portion of the piston 30 in the drawing frictionally or cohesively thereto.
- the integral piston 30 has essentially two diameters (without reference numerals). In an axially middle region of the piston 30, the piston 30 has a comparatively large diameter, which substantially corresponds to an inner diameter of the cylinder liner 32. In one of the working space 25 facing end portion and in a lower end portion in the drawing of the piston 30, this each has a reduced diameter.
- the lower end portion of the piston 30 is radially enclosed by a piston seal 76 held by the seal carrier 64, so that leakage of fuel from the piston pump 24 into the mounting structure or, conversely, leakage of liquid media (eg engine oil) from the mounting structure into the piston pump 24 can be prevented or at least minimized.
- liquid media eg engine oil
- the piston pump 24 can - depending on hydraulic pressures and an axial movement or position of the piston 30 and depending on a state of the quantity control valve 22 and the exhaust valve - fuel from the low pressure line 18 via the inlet nozzle 54 first in the damper chamber 62 and then the radial bores 57a and 57b to the Inlet of the quantity control valve 22 and then flow into the working space 25.
- fuel can be delivered from the working space 25 into the high-pressure line 26 under pressure.
- the radially projecting edge portion 52 of the outer housing shell 50 is formed as a mounting flange 74.
- the mounting flange 74 For attachment of the piston pump 24 to the mounting structure of the internal combustion engine, the mounting flange 74 has two circular holes 77 through which screws (not shown) can be inserted.
- the mounting flange 74 is fluid-tightly connected to the seal carrier 64, in the present case welded. As a result, the mechanical stability of the mounting flange 74 is additionally improved.
- FIG. 4 shows a second embodiment of the piston pump 24.
- the inner housing core 46 of the piston pump 24 according to FIG. 4 manufactured by a method of metal powder injection molding.
- the inner housing core 46 may alternatively be designed by means of precision casting.
- FIG. 4 An Indian FIG. 4 lower end portion of the inner housing core 46 is concentric with the longitudinal axis 44 to a piston 30 radially enclosing collar (without reference numerals) formed.
- the cylinder liner 32 is formed, wherein the guide opening is machined in the usual manner by machining.
- a separate cylinder liner 32 is in accordance with the embodiment FIG. 4 not required.
- FIG. 5 To recognize that the inner housing core 46 is constructed very compact. This results in a particularly small space or a particularly small mass for the inner housing core 46 and thus for the piston pump 24 in total.
- the piston pump 24 can be constructed with fewer components, with a Zerspanungsaufwand is eliminated or minimized.
- FIGS. 6 and 7 together describe a third embodiment of the piston pump 24, including a modification.
- the inner housing core 46 is according to the FIGS. 6 and 7 executed substantially as a cylindrical disc 82, wherein an axis of the cylindrical disc 82 in parallel - in this case even concentric - is arranged to the longitudinal axis 44 of the piston pump 24.
- the cylindrical disc 82 is similar to the embodiment of the inner housing core 46 according to FIG. 2 , made by machining.
- FIG. 7 shows a radial sectional view of the piston pump 24 similar to a plan view to the illustration according to FIG. 6 , However, in contrast to the FIG. 6 -
- the quantity control valve 22 and the outlet port 60 at an angle 86 to each other.
- the angle 86 is defined radially about the longitudinal axis 44 and is presently 120 degrees.
- FIG. 7 a radially outer flattening 88 of the cylindrical disc visible.
- the flattening 88 allows a hydraulic connection between the damper space 62 and the step room 63.
- two each at right angles to the radial bores 57a and 57b (FIG. FIG. 6 ) executed radial holes 57c and 57d visible.
- angle 86 can also have a value other than 120 degrees within comparatively wide limits. This is made possible in particular by the embodiment of the inner housing core 46 as a cylindrical disk 82.
- FIGS. 8 and 9 together show an embodiment of the outer housing shell 50 of the piston pump 24 with a substantially round running shell cross-section. Similar to the embodiments according to the FIGS. 2 to 7 the radially projecting edge portion 52 of the outer housing shell 50 is formed as a mounting flange 74. At two radially opposite regions of the outer housing shell 50, this has two flats 90 on. The flats 90 allow in particular a defined arrangement or assembly of the inner Housing core 46 and the quantity control valve 22 and the outlet port 60 on the outer housing shell 50th
- FIGS. 10 and 11 together show a further embodiment of the outer housing shell 50 of the piston pump 24 with a substantially hexagonal shell cross-section.
- the flattening 90 required for the arrangement of the quantity control valve 22 and the outlet nozzle 60 (see FIGS FIGS. 8 and 9 ) by itself through the side surfaces of the hexagon.
- the piston pump 24, the outer housing shell 50 is designed as a radially symmetrical polygon, in particular as a square, pentagon or octagon.
- FIG. 12 shows a further embodiment of the outer housing shell 50 of the piston pump 24 with a trained as Pratz mounting flange 74.
- the mounting flange 74 is in the FIG. 12 a separate part and is rigidly connected to the - in this case radially comparatively short - radially projecting edge portion 52 of the outer housing shell 50, as will be explained below.
- the seal carrier 64 is additionally arranged in an embodiment modified with respect to the above-described figures.
- the outer housing shell 50 and the seal carrier 64 are both essentially rotationally symmetrical or radially symmetrical to the longitudinal axis 44.
- the seal carrier 64 in the drawing upwardly axially projecting collar 94, with which it is connected to the outer housing shell 50.
- the outer housing shell 50 - and also the seal carrier 64 - at least partially by a plastic deformation, in particular by deep drawing produced.
- FIG. 12 Other elements of the piston pump 24 are in the FIG. 12 for the sake of clarity not shown.
- the preparation of the in the FIG. 12 shown elements such that in a first step, the mounting flange 74 by means of a press connection 96 radially outward with a lower in the drawing shell portion of the outer housing shell 50 is connected.
- a radially circumferential welded joint 98 is then produced from below below between the radially projecting edge section 52 of the outer housing jacket 50 and a radially inner section of the fastening flange 74.
- the seal carrier 64 may be connected to the outer housing shell 50.
- the axially projecting collar 94 of the seal carrier 64 is pressed with a lower radial inner portion of the outer housing jacket 50 in the drawing.
- the press connection produced in this way is then additionally secured by means of a preferably radially circumferential welded connection.
- the seal carrier 64 has a circular opening 100 arranged centrally with respect to the longitudinal axis 44, through which the piston 30 can protrude (not shown).
- FIG. 13 shows a fourth embodiment of the piston pump 24.
- the mounting flange 74 similar to the FIGS. 2 to 11 - Executed essentially by the radially projecting edge portion 52 of the outer housing shell 50.
- the seal carrier 64 is presently connected to a lower axial end portion of the outer housing shell 50 in the drawing, for which the radially projecting edge portion 52 has an additional circumferential characteristic, see the drawing.
- the connection is made by welding, for example by means of a radially encircling I-seam or fillet weld, as in the FIG. 13 designated by an arrow 101.
- the connection between the seal carrier 64 and the outer housing shell 50 is also possible by means of a through-welding.
- FIG. 14 shows a fifth embodiment of the piston pump 24.
- the seal carrier 64 similar to the FIG. 12 - In the drawing upwardly axially projecting collar 94, by means of which it is connected to a radially inner portion of an axial end portion of the outer housing shell 50.
- this connection takes place in a first manufacturing step by pressing and is additionally secured in a second manufacturing step by means of a weld.
- this is an I-seam.
- a Jerusalemsch spaung is, comparable to the FIG. 13 possible.
- the connection between the outer housing shell 50 and the seal carrier 64 is in the FIG. 14 indicated by an arrow 102.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Details Of Reciprocating Pumps (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung betrifft eine Kolbenpumpe nach dem Oberbegriff des Anspruchs 1.The invention relates to a piston pump according to the preamble of claim 1.
Vom Markt und beispielsweise von der
Das der Erfindung zugrunde liegende Problem wird durch eine Kolbenpumpe nach Anspruch 1 gelöst. Vorteilhafte Weiterbildungen sind in Unteransprüchen angegeben. Für die Erfindung wichtige Merkmale finden sich ferner in der nachfolgenden Beschreibung und in den Zeichnungen, wobei die Merkmale sowohl in Alleinstellung als auch in unterschiedlichen Kombinationen für die Erfindung wichtig sein können, wie in den beigefügten Ansprüchen definiert, ohne dass hierauf nochmals explizit hingewiesen wird.The problem underlying the invention is achieved by a piston pump according to claim 1. Advantageous developments are specified in subclaims. For the invention important features can be further found in the following description and in the drawings, the features both alone and in different combinations for the The invention may be important as defined in the appended claims, without being explicitly referred to again.
Die Erfindung weist den Vorteil auf, dass ein Gewicht einer als Kolbenpumpe ausgeführten Kraftstoff-Hochdruckpumpe reduziert sowie Materialkosten und Herstellkosten gesenkt werden können. Insbesondere kann eine Materialmenge in solchen Bereichen der Kolbenpumpe reduziert werden, welche für die Funktion der Kolbenpumpe wenig von Bedeutung und für die Festigkeit wenig kritisch sind. Massiv ausgeführte Elemente der Kolbenpumpe, beispielsweise ein innerer Gehäusekern, werden vorzugsweise (nur) in einem Hochdruckbereich der Kolbenpumpe verwendet. Entsprechend können in einem Niederdruckbereich der Kolbenpumpe vergleichsweise dünnwandige Elemente verwendet werden. Zugleich können sich dadurch funktionale Vorteile im Betrieb der Kolbenpumpe ergeben. Ebenso kann die Anzahl von Elementen der Kolbenpumpe reduziert werden, wobei ein Befestigungsflansch und ein Deckel der Kolbenpumpe in einen äußeren Gehäusemantel integriert werden. Dies kann vorzugsweise einstückig erfolgen.The invention has the advantage that a weight of a fuel high-pressure pump designed as a piston pump can be reduced, and material costs and production costs can be reduced. In particular, a quantity of material in such areas of the piston pump can be reduced, which are of little importance for the function of the piston pump and less critical for the strength. Massively designed elements of the piston pump, for example an inner housing core, are preferably used (only) in a high-pressure region of the piston pump. Accordingly, comparatively thin-walled elements can be used in a low-pressure region of the piston pump. At the same time, this can result in functional advantages in the operation of the piston pump. Likewise, the number of elements of the piston pump can be reduced, wherein a mounting flange and a lid of the piston pump are integrated into an outer housing shell. This can preferably be done in one piece.
Weiterhin weist die erfindungsgemäße Kolbenpumpe vergleichsweise große Raumabschnitte auf, welche im Betrieb mit Kraftstoff gefüllt sind. Dadurch wird es ermöglicht, dass Elemente bzw. Fluidbereiche innerhalb der Kolbenpumpe miteinander besser hydraulisch verbunden sein können. Beispielsweise betrifft dies einen so genannten "Dämpferraum" und einen "Stufenraum" der Kolbenpumpe sowie eine hydraulische Verbindung zu einem Mengensteuerventil. Dabei können sich geringere Saugverluste der Kolbenpumpe sowie eine bessere Befüllung eines Arbeitsraums der Kolbenpumpe ergeben. Dadurch kann eine Dampfbildung innerhalb der Kolbenpumpe vermindert werden, wodurch sich eine geringere Gefahr von Kolbenfressern ergeben kann. Gegebenenfalls kann ein Vordruck der erfindungsgemäßen Kolbenpumpe abgesenkt werden. Weiterhin umschließt die Kolbenpumpe bzw. der äußere Gehäusemantel ein vergleichsweise großes Kraftstoffvolumen, wodurch hydraulische Pulsationen in dem Niederdruckbereich der Kolbenpumpe besser gedämpft werden können.Furthermore, the piston pump according to the invention has comparatively large space sections which are filled with fuel during operation. This makes it possible that elements or fluid areas within the piston pump can be better hydraulically connected to each other. For example, this relates to a so-called "damper space" and a "step space" of the piston pump and a hydraulic connection to a quantity control valve. This can result in lower suction losses of the piston pump and a better filling of a working space of the piston pump. As a result, a vapor formation can be reduced within the piston pump, which may result in a lower risk of seizure. Optionally, a pre-pressure of the piston pump according to the invention can be lowered. Furthermore, the piston pump or the outer housing jacket encloses a comparatively large volume of fuel, whereby hydraulic pulsations in the low-pressure region of the piston pump can be better damped.
Weiterhin wird im Betrieb eine im Wesentlichen gleichmäßige und schnelle Erwärmung eines Kolbens und einer Zylinderbuchse der Kolbenpumpe ermöglicht, weil die Zylinderbuchse vergleichsweise wenige bzw. kleinflächige Verbindungsabschnitte zu übrigen Elementen der Kolbenpumpe aufweist. Dadurch wird ebenfalls eine verminderte Neigung zu Kolbenfressern erreicht. Weiterhin kann die erfindungsgemäße Kolbenpumpe mit einem geringeren Aufwand an spanender Bearbeitung hergestellt werden. Elemente der Kolbenpumpe - insbesondere in dem Niederdruckbereich - können als vergleichsweise einfach hergestellte Drehteile oder als Blech-Tiefziehteile ausgeführt werden. Dies ist erfindungsgemäß ebenfalls für einen so genannten "Kundenanschluss" möglich, mittels dessen die Kolbenpumpe beispielsweise in eine Anbaustruktur einer Brennkraftmaschine montiert werden kann.Furthermore, during operation, a substantially uniform and rapid heating of a piston and a cylinder liner of the piston pump allows, because the cylinder liner has comparatively few or small-area connecting portions to other elements of the piston pump. As a result, a reduced tendency to seizure is also achieved. Furthermore, the piston pump according to the invention can be manufactured with a lower cost of machining. Elements of the piston pump - in particular in the low-pressure region - can be designed as relatively simply produced turned parts or as sheet-metal deep-drawn parts. This is also possible according to the invention for a so-called "customer connection", by means of which the piston pump can be mounted, for example, in a mounting structure of an internal combustion engine.
Die Erfindung betrifft eine Kolbenpumpe, insbesondere Hochdruckpumpe für ein Kraftstoffsystem für eine Brennkraftmaschine, mit einem inneren Gehäusekern, an dem eine Zylinderbuchse befestigt ist (was einschließt, dass der innere Gehäusekern die Zylinderbuchse bildet), und mit einem äußeren Gehäusemantel, welcher mindestens abschnittsweise den inneren Gehäusekern von radial außen umhüllt. Erfindungsgemäß bildet mindestens ein radial abragender Randabschnitt des äußeren Gehäusemantels mindestens einen Teil eines Befestigungsflansches, mit dem die Kolbenpumpe an einer Anbaustruktur befestigt werden kann. Auf diese Weise sind der äußere Gehäusemantel sowie mindestens ein Teil des Befestigungsflansches als gemeinsames Teil ausgeführt. Dadurch können die Anzahl der Elemente der Kolbenpumpe gesenkt, die Herstellung vereinfacht und Kosten vermindert werden. Weiterhin kann eine Rohmaterialmenge reduziert werden. Beispielsweise kann der innere Gehäusekern aus einem Rohling hergestellt werden, welcher nur etwa ein Viertel der Materialmenge eines vergleichbaren herkömmlichen Elements erfordert.The invention relates to a piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine, with an inner housing core to which a cylinder liner is attached (which includes that the inner housing core forms the cylinder liner), and with an outer housing shell, which at least partially the inner Housing core surrounded by radially outside. According to the invention, at least one radially projecting edge section of the outer housing shell forms at least one part of a fastening flange with which the piston pump can be fastened to a mounting structure. In this way, the outer housing shell and at least a part of the mounting flange are designed as a common part. Thereby, the number of elements of the piston pump can be reduced, the production is simplified and costs are reduced. Furthermore, a quantity of raw material can be reduced. For example, the inner housing core can be made from a blank which requires only about one fourth of the amount of material of a comparable conventional element.
In einer Ausgestaltung der Kolbenpumpe ist vorgesehen, dass der radial abragende Randabschnitt ein separates Teil und mit einem Mantelabschnitt des Gehäusemantels verpresst und/oder verschweißt ist. Dadurch wird es ermöglicht, den radial abragenden Randabschnitt, hier also den Befestigungsflansch, und den äußeren Gehäusemantel aus verschiedenen Werkstoffen und/oder mit verschiedenen Materialstärken auszuführen, so dass beide Elemente jeweils für sich optimiert sein können. Insbesondere ist es dadurch möglich, die Steifigkeit des Befestigungsflansches zu erhöhen, wodurch die Funktion der Kolbenpumpe verbessert wird. Erfindungsgemäß ist vorgesehen, dass der Gehäusemantel einen Halterungsabschnitt aufweist, der radial innen eine Kolbendichtung und/oder radial außen eine O-Ringdichtung und/oder axial außen eine Kolbenfeder haltert. Dadurch kann der äußere Gehäusemantel auf einfache Weise für eine Befestigung weiterer Elemente der Kolbenpumpe verwendet werden, so dass entsprechende separate Halterungen entfallen können. Die den Kolben radial außen umschließende Kolbendichtung kann einen Arbeitsraum der Kolbenpumpe nach außen abdichten. Die O-Ringdichtung ermöglicht es, die Kolbenpumpe insgesamt gegen die Anbaustruktur bzw. eine Öffnung der Anbaustruktur, in die die Kolbenpumpe eingesetzt ist, nach außen abzudichten. Die Kolbenfeder wirkt einer Kraft einer an einem stirnseitigen Abschnitt des Kolbens angreifenden Nocke entgegen. Dadurch wird die erfindungsgemäße Kolbenpumpe insgesamt vereinfacht und verbilligt. Erfindungsgemäß ist vorgesehen, dass der Halterungsabschnitt ein separates Teil und an einen Mantelabschnitt des Gehäusemantels axial oder radial angeschweißt und/oder mit diesem axial oder radial verpresst ist. Beispielsweise wird es dadurch ermöglicht, den Halterungsabschnitt mit einer anderen Materialstärke auszuführen. Dadurch ist der Halterungsabschnitt spezifisch an seine jeweilige Funktion angepasst, wodurch die Kolbenpumpe insgesamt verbessert und Gewicht sowie Material und schlussendlich Kosten gespart werden.In one embodiment of the piston pump is provided that the radially projecting edge portion is pressed a separate part and with a jacket portion of the housing shell and / or welded. This makes it possible to carry out the radially projecting edge portion, in this case the mounting flange, and the outer housing shell made of different materials and / or with different material thicknesses, so that both elements can be optimized for themselves. In particular, it is thereby possible to increase the rigidity of the mounting flange, whereby the function of the piston pump is improved. According to the invention, it is provided that the housing jacket has a holding section which radially inwardly supports a piston seal and / or radially outwardly an O-ring seal and / or axially outside a piston spring. As a result, the outer housing shell can be used in a simple manner for attachment of further elements of the piston pump, so that corresponding separate holders can be omitted. The piston radially outwardly surrounding piston seal can seal a working space of the piston pump to the outside. The O-ring seal makes it possible to seal the piston pump as a whole against the mounting structure or an opening of the mounting structure, in which the piston pump is inserted to the outside. The piston spring counteracts a force of an acting on an end portion of the piston cam. As a result, the piston pump according to the invention is simplified and cheaper overall. According to the invention it is provided that the support portion is a separate part and welded to a shell portion of the housing shell axially or radially and / or compressed axially or radially with this. For example, this makes it possible to carry out the mounting portion with a different material thickness. As a result, the support portion is specifically adapted to its respective function, whereby the piston pump improved overall and weight and material and ultimately costs are saved.
In einer weiteren Ausgestaltung der Kolbenpumpe ist der äußere Gehäusemantel mindestens bereichsweise mittels plastischer Verformung, insbesondere mittels Tiefziehen hergestellt. Dadurch kann der Gehäusemantel besonders einfach und zugleich kostengünstig hergestellt werden.In a further embodiment of the piston pump, the outer housing shell is at least partially made by means of plastic deformation, in particular by deep drawing. As a result, the housing shell can be produced in a particularly simple and cost-effective manner.
Weiterhin kann vorgesehen sein, dass in mindestens einem Raumabschnitt zwischen dem äußeren Gehäusemantel einerseits und dem inneren Gehäusekern andererseits mindestens eine mit einem Niederdruckanschluss verbundene Fluidkammer ausgebildet ist. Dadurch kann das innerhalb der Kolbenpumpe vorhandene Kraftstoffvolumen vergrößert werden, wodurch sich eine verbesserte Pulsationsdämpfung in einem Niederdruckbereich der Kolbenpumpe bzw. des Kraftstoffsystems ergeben kann.Furthermore, provision may be made for at least one fluid chamber connected to a low-pressure connection to be formed in at least one space section between the outer housing shell on the one hand and the inner housing core on the other hand. As a result, the fuel volume present within the piston pump can be increased, which can result in improved pulsation damping in a low-pressure region of the piston pump or of the fuel system.
In einer weiteren Ausgestaltung der Kolbenpumpe ist der innere Gehäusekern wenigstens abschnittsweise im Wesentlichen zylinderförmig oder als Flachstab ausgeführt, wobei eine Achse des Zylinders oder Flachstabs senkrecht zu einer Längsachse der Kolbenpumpe angeordnet ist. Beispielsweise ist der innere Gehäusekern im Wesentlichen als massives Bauteil ausgeführt, welches mittels spanender Nachbearbeitung in eine jeweils gewünschte Form gebracht wird. Vorzugsweise sind an den Stirnseiten des Zylinders oder Flachstabs ein Einlassventil und ein Auslassventil der erfindungsgemäßen Kolbenpumpe angeordnet. Weiterhin kann eine Zylinderbuchse der Kolbenpumpe in dem besagten Zylinder oder Flachstab zumindest teilweise angeordnet sein. Dabei ist die Zylinderbuchse beispielsweise senkrecht zu der Achse des Zylinders oder Flachstabs angeordnet. Durch die - vorzugsweise - massive Ausführung des Zylinders oder Flachstabs ist dieser besonders gut für hohe Kraftstoffdrücke geeignet. Die zylindrische Form an sich kann Vorteile für die Montage des Einlassventils und des Auslassventils aufweisen.In a further embodiment of the piston pump, the inner housing core is at least partially substantially cylindrical or designed as a flat bar, wherein an axis of the cylinder or flat bar is arranged perpendicular to a longitudinal axis of the piston pump. For example, the inner housing core is designed substantially as a solid component, which is brought by means of cutting reworking in a desired shape. Preferably, an inlet valve and an outlet valve of the piston pump according to the invention are arranged on the end faces of the cylinder or flat bar. Furthermore, a cylinder liner of the piston pump in the said cylinder or flat bar can be at least partially arranged. In this case, the cylinder liner is arranged, for example, perpendicular to the axis of the cylinder or flat bar. Due to the - preferably - solid design of the cylinder or flat bar this is particularly well suited for high fuel pressures. The cylindrical shape itself may have advantages for the assembly of the inlet valve and the outlet valve.
In einer dazu alternativen Ausgestaltung der Kolbenpumpe ist der innere Gehäusekern im Wesentlichen als zylindrische Scheibe ausgeführt, wobei eine Achse der zylindrischen Scheibe parallel oder sogar koaxial zu einer Längsachse der Kolbenpumpe angeordnet ist. Insbesondere wird dadurch ermöglicht, dass hydraulische Anschlüsse der Kolbenpumpe in einem zu einer Längsachse der Kolbenpumpe definierten Winkel angeordnet sein können. Dabei kann der Winkel konstruktiv vergleichsweise beliebig gewählt werden. Der derart ausgebildete innere Gehäusekern kann besonders einfach und dauerhaft an radial inneren Abschnitten des äußeren Gehäusemantels angeordnet bzw. mit diesen verbunden sein. Dadurch kann die Robustheit der erfindungsgemäßen Kolbenpumpe verbessert werden.In an alternative embodiment of the piston pump of the inner housing core is designed substantially as a cylindrical disc, wherein an axis of the cylindrical disc is arranged parallel or even coaxial with a longitudinal axis of the piston pump. In particular, this makes it possible that hydraulic connections of the piston pump can be arranged in an angle defined to a longitudinal axis of the piston pump. The angle can be structurally chosen comparatively arbitrary. The thus formed inner housing core can be particularly easily and permanently disposed on radially inner portions of the outer housing shell or connected thereto. As a result, the robustness of the piston pump according to the invention can be improved.
Weiterhin kann vorgesehen sein, dass der innere Gehäusekern mittels spanender Bearbeitung ausgeführt ist. Der innere Gehäusekern stellt sozusagen ein zentrales Element der erfindungsgemäßen Kolbenpumpe dar. Mittels der spanenden Bearbeitung kann der innere Gehäusekern daher spezifisch ausgebildet sein, wodurch die Verbindung zu übrigen Elementen der Kolbenpumpe verbessert werden kann.Furthermore, it can be provided that the inner housing core is carried out by means of machining. The inner housing core, so to speak, represents a central element of the piston pump according to the invention. By means of the machining, the inner housing core can therefore be designed specifically, whereby the connection to other elements of the piston pump can be improved.
Die Herstellung der Kolbenpumpe kann verbilligt werden, wenn der innere Gehäusekern mit einem Verfahren des Metall-Pulverspritzgießens (engl. MIM, "metal injection molding") oder mittels Feinguss ausgeführt ist. Dadurch kann die Anzahl der Arbeitsschritte zur Herstellung des inneren Gehäusekerns gesenkt werden, wodurch sich Kostenvorteile ergeben können.The manufacture of the piston pump can be made cheaper if the inner casing core is made by a method of metal injection molding (MIM) or by precision casting. Thereby, the number of steps for the production of the inner housing core can be reduced, which can result in cost advantages.
In einer weiteren Ausgestaltung der Kolbenpumpe ist ein Mantelabschnitt des äußeren Gehäusemantels in einer Ebene senkrecht zu einer Längsachse der Kolbenpumpe im Wesentlichen als radialsymmetrisches Vieleck ausgeführt. Dadurch weist der äußere Gehäusemantel abschnittsweise plane Flächen aus, an welchen hydraulische Anschlüsse der Kolbenpumpe besonders gut angeordnet sein können. Beispielsweise ist das Vieleck ein Sechseck.In a further embodiment of the piston pump, a jacket section of the outer housing jacket is designed substantially as a radially symmetrical polygon in a plane perpendicular to a longitudinal axis of the piston pump. As a result, the outer housing shell sections partially planar surfaces, on which hydraulic connections of the piston pump can be particularly well arranged. For example, the polygon is a hexagon.
Nachfolgend werden beispielhafte Ausführungsformen der Erfindung unter Bezugnahme auf die Zeichnung erläutert. In der Zeichnung zeigen:
- Figur 1
- ein vereinfachtes Schema für ein Kraftstoffsystem für eine Brennkraftmaschine;
- Figur 2
- einen teilweisen Längsschnitt durch eine erste Ausführungsform einer Kolbenpumpe für das Kraftstoffsystem von
Figur 1 ; - Figur 3
- einen teilweisen Schnitt längs der Linie III-III von
Figur 2 ; - Figur 4
- eine Darstellung ähnlich zu
Figur 2 einer zweiten Ausführungsform der Kolbenpumpe; - Figur 5
- einen teilweisen Schnitt längs der Linie V-V von
Figur 4 ; - Figur 6
- eine Darstellung ähnlich zu
Figur 2 einer dritten Ausführungsform der Kolbenpumpe; - Figur 7
- einen teilweisen Schnitt längs der Linie VII-VII der Darstellung von
Figur 6 , wobei ein Mengensteuerventil und ein Auslassstutzen allerdings in einem Winkel von 120° angeordnet sind; - Figur 8
- eine Seitenansicht eines äußeren Gehäusemantels der Kolbenpumpen der
Figuren 2 bis 6 mit einem im Wesentlichen rund ausgeführten Mantelquerschnitt; - Figur 9
- einen Schnitt längs einer Linie IX-IX von
Figur 8 ; Figur 10- eine Seitenansicht einer zweiten Ausführungsform des äußeren Gehäusemantels mit einem im Wesentlichen sechseckig ausgeführten Mantelquerschnitt;
- Figur 11
- einen Schnitt längs einer Linie XI-
XI von Figur 10 ; Figur 12- einen Längsschnitt durch eine dritte Ausführungsform des äußeren Gehäusemantels mit einem als Pratz ausgeführten Befestigungsflansch;
- Figur 13
- einen teilweisen Längsschnitt durch eine vierte Ausführungsform der Kolbenpumpe; und
Figur 14- eine Darstellung ähnlich zu
Figur 2 einer fünften Ausführungsform der Kolbenpumpe.
- FIG. 1
- a simplified diagram for a fuel system for an internal combustion engine;
- FIG. 2
- a partial longitudinal section through a first embodiment of a piston pump for the fuel system of
FIG. 1 ; - FIG. 3
- a partial section along the line III-III of
FIG. 2 ; - FIG. 4
- a representation similar to
FIG. 2 a second embodiment of the piston pump; - FIG. 5
- a partial section along the line VV of
FIG. 4 ; - FIG. 6
- a representation similar to
FIG. 2 a third embodiment of the piston pump; - FIG. 7
- a partial section along the line VII-VII of the representation of
FIG. 6 However, a quantity control valve and an outlet are arranged at an angle of 120 °; - FIG. 8
- a side view of an outer housing shell of the piston pumps of
FIGS. 2 to 6 with a substantially circular shell cross-section; - FIG. 9
- a section along a line IX-IX of
FIG. 8 ; - FIG. 10
- a side view of a second embodiment of the outer housing shell with a substantially hexagonal shell cross section;
- FIG. 11
- a section along a line XI-XI of
FIG. 10 ; - FIG. 12
- a longitudinal section through a third embodiment of the outer housing shell with a designed as a prüf mounting flange;
- FIG. 13
- a partial longitudinal section through a fourth embodiment of the piston pump; and
- FIG. 14
- a representation similar to
FIG. 2 a fifth embodiment of the piston pump.
Es werden für funktionsäquivalente Elemente und Größen in allen Figuren auch bei unterschiedlichen Ausführungsformen die gleichen Bezugszeichen verwendet.The same reference numerals are used for functionally equivalent elements and sizes in all figures, even in different embodiments.
Weiterhin sind eine Zylinderbuchse 32, ein in der Zylinderbuchse 32 angeordneter Kolben 30 und ein von der Zylinderbuchse 32 umschlossener Arbeitsraum 25, sowie eine an einem axialen Endabschnitt 38 des Kolbens 30 angreifende Nockenscheibe 40 in der
Es versteht sich, dass das Mengensteuerventil 22 auch als Baueinheit mit der Kolbenpumpe 24 ausgebildet sein kann, wie in den nachfolgenden
Beim Betrieb des Kraftstoffsystems 10 fördert die Vorförderpumpe 16 Kraftstoff vom Kraftstofftank 12 in die Niederdruckleitung 18. Das Mengensteuerventil 22 kann in Abhängigkeit von einem jeweiligen Bedarf an Kraftstoff geschlossen und geöffnet werden. Hierdurch wird die in den Hochdruckspeicher 28 geförderte Kraftstoffmenge beeinflusst. Der Kraftstoff ist beispielsweise Benzin oder Dieselkraftstoff.During operation of the
Weiterhin weist die Kolbenpumpe 24 einen im Wesentlichen topfförmig ausgeführten dünnwandigen äußeren Gehäusemantel 50 auf, welcher unter anderem den inneren Gehäusekern 46 von radial außen umhüllt. Der innere Gehäusekern 46 der Kolbenpumpe 24 gemäß
Ein in der Zeichnung unterer Randabschnitt 52 des äußeren Gehäusemantels 50 ist radial leicht nach außen abragend wellenförmig gebogen. Wie in der
In der Zeichnung oben ist an dem äußeren Gehäusemantel 50 ein Zulaufstutzen 54 angeordnet und fluiddicht mit dem äußeren Gehäusemantel 50 verbunden. Der Zulaufstutzen 54 ist rotationssymmetrisch zu der Längsachse 44 der Kolbenpumpe 24 ausgeführt bzw. angeordnet. In einem in der Zeichnung oberen Abschnitt des äußeren Gehäusemantels 50 umschließt dieser einen Druckdämpfer 56, vorliegend einen Membrandruckdämpfer.In the drawing above, an
Der innere Gehäusekerns 46 weist koaxial zur Längsachse 48 jeweils eine erste Stufenbohrung (ohne Bezugszeichen) bzw. eine zweite Stufenbohrung (ohne Bezugszeichen) auf, die beide in eine zur Längsachse 44 koaxiale Sackbohrung (ohne Bezugszeichen) münden, in die die Zylinderbuchse 32 eingepresst ist. In der ersten Bohrung (in der Zeichnung links) im inneren Gehäusekern 46 ist ein Abschnitt eines Auslassstutzens 60 angeordnet, in den ein Auslassventil integriert ist. In der zweiten Bohrung (in der Zeichnung rechts) ist ein Abschnitt des Mengensteuerventils 22 angeordnet. Der Auslassstutzen 60 ist mit der Hochdruckleitung 26 (siehe
Ein im Bereich des Druckdämpfers 56 vorhandener Raumabschnitt zwischen dem äußeren Gehäusemantel 50 einerseits und dem inneren Gehäusekern 46 andererseits bildet einen so genannten Dämpferraum 62 ("Fluidkammer"), welcher mit einem an die Niederdruckleitung 18 anschließbaren Niederdruckanschluss 58 hydraulisch verbunden ist. Ein in der Zeichnung unterhalb des inneren Gehäusekerns 46 vorhandener Raumabschnitt bildet einen so genannten Stufenraum 63. Der innere Gehäusekern 46 weist in einem dem Mengensteuerventil 22 zugewandten axialen Endabschnitt radiale Bohrungen 57a und 57b auf, welche einen Einlass des Mengensteuerventils 22 mit dem Dämpferraum 62 sowie mit dem Stufenraum 63 hydraulisch verbinden.An existing in the region of the
An einem in der Zeichnung von
Vorliegend sind der Dichtungsträger 64, der Dichtungshalter 66 und der innere Halterungsabschnitt 68 unter Verwendung von gezogenen bzw. geprägten gebogenen Blechen (Tiefziehteile) hergestellt. Weil diese Elemente den Stufenraum 63 begrenzen, welcher einen vergleichsweise niedrigen hydraulischen Druck aufweist, sind diese Elemente vergleichsweise dünn und leicht ausgeführt. Die drei besagten Elemente berühren einander zumindest paarweise oder sind zumindest bereichsweise und paarweise kraftschlüssig oder stoffschlüssig miteinander verbunden. Insbesondere ist der Dichtungshalter 66 in einem radial inneren Bereich als Ringscheibe ausgeführt, wobei Abschnitte des Dichtungsträgers 64 und des inneren Halterungsabschnitts 68 durch ein zentrisch in dem Dichtungshalter 66 angeordnetes Loch ragen.In the present case, the
In einer umlaufenden radial einwärtigen Ausprägung des Dichtungsträgers 64 ist eine Gehäusedichtung 70, welche vorliegend als O-Ringdichtung ausgeführt ist, angeordnet. Dabei bildet die umlaufende Ausprägung des Dichtungsträgers 64 zusammen mit einem radial äußeren Randabschnitt des Dichtungshalters 66 eine radial umlaufende Nut, in welcher die Gehäusedichtung 70 formschlüssig gehalten ist. Der Dichtungsträger 64 ist mit einem in der
In einem unteren Bereich von
Der einstückig ausgeführte Kolben 30 weist im Wesentlichen zwei Durchmesser (ohne Bezugszeichen) auf. In einem axial mittleren Bereich des Kolbens 30 weist der Kolben 30 einen vergleichsweise großen Durchmesser auf, welcher im Wesentlichen einem Innendurchmesser der Zylinderbuchse 32 entspricht. In einem dem Arbeitsraum 25 zugewandten Endabschnitt sowie in einem in der Zeichnung unteren Endabschnitt des Kolbens 30 weist dieser jeweils einen verminderten Durchmesser auf. Der untere Endabschnitt des Kolbens 30 wird von einer von dem Dichtungsträger 64 gehaltenen Kolbendichtung 76 radial umschlossen, so dass eine Leckage von Kraftstoff aus der Kolbenpumpe 24 in die Anbaustruktur bzw. umgekehrt eine Leckage von flüssigen Medien (beispielsweise Motorenöl) aus der Anbaustruktur in die Kolbenpumpe 24 verhindert oder zumindest minimiert werden kann.The
Im Betrieb der Kolbenpumpe 24 kann - abhängig von hydraulischen Drücken und einer axialen Bewegung bzw. Position des Kolbens 30 sowie abhängig von einem Zustand des Mengensteuerventils 22 und des Auslassventils - Kraftstoff aus der Niederdruckleitung 18 über den Zulaufstutzen 54 zunächst in den Dämpferraum 62 und dann durch die radialen Bohrungen 57a und 57b zu dem Einlass des Mengensteuerventils 22 und danach in den Arbeitsraum 25 strömen. Ebenso kann - abhängig von hydraulischen Drücken und der axialen Bewegung bzw. Position des Kolbens 30 sowie abhängig von dem Zustand des Mengensteuerventils 22 und des Auslassventils - Kraftstoff aus dem Arbeitsraum 25 in die Hochdruckleitung 26 unter Druck gefördert werden.During operation of the
Insbesondere in der
Ein in der
Zusammen mit der Darstellung von
Die
Die
Weiterhin ist in der
Man erkennt, dass der Winkel 86 in vergleichsweise weiten Grenzen auch einen anderen Wert als 120 Grad aufweisen kann. Dies wird insbesondere durch die Ausführung des inneren Gehäusekerns 46 als zylindrische Scheibe 82 ermöglicht.It can be seen that the
Die
Die
Der äußere Gehäusemantel 50 und der Dichtungsträger 64 sind beide im Wesentlichen rotationssymmetrisch bzw. radialsymmetrisch zu der Längsachse 44 ausgeführt. Vorliegend weist der Dichtungsträger 64 einen in der Zeichnung nach oben axial abragenden Kragen 94 auf, mit welchem er mit dem äußeren Gehäusemantel 50 verbunden ist. Wie schon bei den
Sonstige Elemente der Kolbenpumpe 24 sind in der
In ähnlicher Weise kann der Dichtungsträger 64 mit dem äußeren Gehäusemantel 50 verbunden werden. Dabei wird in einem ersten Schritt der axial abragende Kragen 94 des Dichtungsträgers 64 mit einem in der Zeichnung unteren radial inneren Abschnitt des äußeren Gehäusemantels 50 verpresst. In einem zweiten Schritt wird danach die derart hergestellte Pressverbindung mittels einer vorzugsweise radial umlaufenden Schweißverbindung zusätzlich gesichert. In einem in der Zeichnung unteren Bereich weist der Dichtungsträger 64 eine zentrisch zu der Längsachse 44 angeordnete kreisförmige Öffnung 100 auf, durch welche der Kolben 30 ragen kann (nicht mit dargestellt).Similarly, the
Die
Claims (9)
- Piston pump (24), in particular high-pressure pump for a fuel system (10) for an internal combustion engine, having an inner housing core (46), to which a cylinder liner (32) is fastened, and having an outer housing shell (50) which encloses the inner housing core (46) at least in sections radially from the outside, at least one radially protruding edge section (52) of the outer housing shell (50) forming at least one part of a fastening flange (74), by way of which the piston pump (24) can be fastened to a mounting structure, characterized in that a securing section (65) is welded axially or radially onto a shell section of the housing shell (50) and/or is pressed axially or radially with the latter, and in that the securing section (65) secures a piston seal (76) radially on the inside and/or an O-ring seal (70) radially on the outside and/or a piston spring (72) axially on the outside.
- Piston pump (24) according to Claim 1, characterized in that the radially protruding edge section (52) a separate part and is pressed with and/or welded to a shell section of the housing shell (50).
- Piston pump (24) according to at least either of the preceding claims, characterized in that the outer housing shell (50) is manufactured at least in regions by means of plastic deformation, in particular by means of deep drawing.
- Piston pump (24) according to at least one of the preceding claims, characterized in that in at least one room section at least one fluid chamber (62) which is connected to a low-pressure connector (58) is configured between the outer housing shell (50) on one side and the inner housing core (46) on the other side.
- Piston pump (24) according to at least one of the preceding claims, characterized in that the inner housing core (46) is configured at least in sections so as to be substantially cylindrical or as a flat bar, an axis (48) of the cylinder or flat bar being arranged perpendicularly with respect to a longitudinal axis (44) of the piston pump (24).
- Piston pump (24) according to at least one of Claims 1 to 4, characterized in that the inner housing core (46) is configured substantially as a cylindrical disc (82), an axis of the cylindrical disc (82) being arranged parallel to a longitudinal axis (44) of the piston pump (24).
- Piston pump (24) according to at least one of the preceding claims, characterized in that the inner housing core (46) is configured by means of machining.
- Piston pump (24) according to at least one of Claims 1 to 6, characterized in that the inner housing core (46) is configured by way of a process of metal powder injection moulding or by means of precision casting.
- Piston pump (24) according to at least one of the preceding claims, characterized in that a shell section of the outer housing shell (50) is configured substantially as a radially symmetrical polygon in a plane perpendicularly with respect to a longitudinal axis (44) of the piston pump (24).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE201310207393 DE102013207393A1 (en) | 2013-04-24 | 2013-04-24 | Piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine |
PCT/EP2014/056043 WO2014173603A1 (en) | 2013-04-24 | 2014-03-26 | Piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2989316A1 EP2989316A1 (en) | 2016-03-02 |
EP2989316B1 true EP2989316B1 (en) | 2017-05-24 |
Family
ID=50389430
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14713093.4A Active EP2989316B1 (en) | 2013-04-24 | 2014-03-26 | Piston pump, in particular high-pressure pump for a fuel system for an internal combustion engine |
Country Status (5)
Country | Link |
---|---|
EP (1) | EP2989316B1 (en) |
KR (1) | KR20160002824A (en) |
CN (1) | CN105143656A (en) |
DE (1) | DE102013207393A1 (en) |
WO (1) | WO2014173603A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2024160457A1 (en) * | 2023-02-02 | 2024-08-08 | Phinia Delphi Luxembourg Sarl | Pump-flange assembly process |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB201418661D0 (en) * | 2014-10-21 | 2014-12-03 | Delphi International Operations Luxembourg S.�.R.L. | Pumping Mechanism |
DE102016204128A1 (en) | 2016-03-14 | 2017-09-14 | Robert Bosch Gmbh | high pressure pump |
DE102016212469A1 (en) * | 2016-07-08 | 2018-01-11 | Robert Bosch Gmbh | Method for producing a high-pressure fuel pump |
DE102018211301A1 (en) * | 2018-07-09 | 2020-01-09 | Robert Bosch Gmbh | Pressure damper for a high pressure fuel pump |
DE102021214628A1 (en) * | 2021-12-17 | 2023-06-22 | Robert Bosch Gesellschaft mit beschränkter Haftung | High pressure pump for a fuel system of an internal combustion engine |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1582735A4 (en) * | 2003-01-09 | 2006-06-07 | Bosch Automotive Systems Corp | Fuel feed pump |
DE10345725B4 (en) * | 2003-10-01 | 2017-01-05 | Robert Bosch Gmbh | High-pressure fuel pump |
CN100587252C (en) * | 2005-09-29 | 2010-02-03 | 株式会社电装 | Fluid pump having plunger and method of monoblock casting for housing of the same |
DE102007038984A1 (en) * | 2007-08-17 | 2009-02-19 | Robert Bosch Gmbh | Fuel pump for a fuel system of an internal combustion engine |
JP2010037997A (en) * | 2008-08-01 | 2010-02-18 | Denso Corp | Fuel supply pump |
JP5081869B2 (en) * | 2009-06-18 | 2012-11-28 | 日立オートモティブシステムズ株式会社 | High pressure fuel supply pump |
US9683559B2 (en) * | 2011-08-01 | 2017-06-20 | Toyota Jidosha Kabushiki Kaisha | Fuel pump |
FI124006B (en) * | 2011-09-30 | 2014-01-31 | Waertsilae Finland Oy | Fuel injection pump arrangement and method for operating an internal combustion engine |
-
2013
- 2013-04-24 DE DE201310207393 patent/DE102013207393A1/en not_active Withdrawn
-
2014
- 2014-03-26 EP EP14713093.4A patent/EP2989316B1/en active Active
- 2014-03-26 CN CN201480023182.2A patent/CN105143656A/en active Pending
- 2014-03-26 KR KR1020157030605A patent/KR20160002824A/en not_active Application Discontinuation
- 2014-03-26 WO PCT/EP2014/056043 patent/WO2014173603A1/en active Application Filing
Non-Patent Citations (1)
Title |
---|
None * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2024160457A1 (en) * | 2023-02-02 | 2024-08-08 | Phinia Delphi Luxembourg Sarl | Pump-flange assembly process |
Also Published As
Publication number | Publication date |
---|---|
DE102013207393A1 (en) | 2014-10-30 |
WO2014173603A1 (en) | 2014-10-30 |
EP2989316A1 (en) | 2016-03-02 |
CN105143656A (en) | 2015-12-09 |
KR20160002824A (en) | 2016-01-08 |
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