WO2005052351A1 - Kraftstoffeinspritzpumpe mit förderverlaufssteurung - Google Patents
Kraftstoffeinspritzpumpe mit förderverlaufssteurung Download PDFInfo
- Publication number
- WO2005052351A1 WO2005052351A1 PCT/EP2004/013044 EP2004013044W WO2005052351A1 WO 2005052351 A1 WO2005052351 A1 WO 2005052351A1 EP 2004013044 W EP2004013044 W EP 2004013044W WO 2005052351 A1 WO2005052351 A1 WO 2005052351A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pump
- recess
- control edge
- injection
- fuel injection
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
- F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
- F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
- F02M45/06—Pumps peculiar thereto
- F02M45/066—Having specially arranged spill port and spill contour on the piston
Definitions
- the present invention relates to a fuel injection pump with the possibility of regulating the course of delivery of an injection.
- it relates to a fuel injection pump for multi-stage injection of fuel in internal combustion engines according to the preamble of claim 1.
- a fuel injection pump with a purely mechanical control of pre-injection and main injection is described, for example, in British Patent Application GB 893,621 dated June 22, 1960.
- the fuel injection pump shown there holds a pump piston, which is arranged in a pump cylinder so that it can move axially and rotatably.
- the pump piston draws fuel through at least one suction hole from the suction chamber into the pump work chamber delimited by the piston piston end face.
- the connection to the suction chamber is first interrupted and the delivery from the pump work chamber is initiated, which then ends by opening a return flow path leading to the suction bore with the aid of a sloping control edge on the pump piston with a limited circumference.
- circumferentially arranged recesses are provided on the pump piston and on the pump cylinder, which are delimited in the axial direction by control edges for controlling the pre-injection and main injection.
- the pre-injection is ended by an interaction of the control edge of the recess in the pump cylinder facing away from the pump work space with the control edge of the recess in the pump piston facing the pump work space by releasing an overflow path from the pump work space to the suction bore.
- the start of the main injection is controlled by an interaction of the control edge of the recess in the pump cylinder facing the pump working space with a control edge on the pump piston.
- a disadvantage of the fuel injection pump shown in GB 893,621 is that two different bores, namely a suction bore and a separate control bore, are formed, the control bore being used to create a low-pressure path to the pump work space. Since the start of the main injection is controlled by an interaction of the control edge of the recess in the pump cylinder facing the pump working space with the control edge of the pump piston end face, design restrictions are imposed on the pump piston.
- the pilot injection is not in terms of quantity adjustable; post-injection is not possible. Zero delivery can only be set, as in a conventional manner, by means of a longitudinal groove that connects the pump work chamber to the suction bore in a fluid-conducting manner.
- the object of the present invention is to provide a fuel pump with a mechanically controlled delivery flow control, by means of which the disadvantages mentioned above can be avoided.
- This object is achieved according to the invention by a fuel injection pump according to claim 1.
- Advantageous embodiments of the invention are specified in the subclaims.
- the fuel injection pump for multi-stage injection of fuel in internal combustion engines comprises at least one pump piston which is arranged in a pump cylinder so as to be axially and rotatably movable.
- the pump piston sucks fuel through at least one suction hole from the suction chamber into the pump work chamber delimited by the pump piston end face.
- the connection to the suction chamber is interrupted by means of an upper main control edge surrounding the pump piston end face and the pumping is initiated from the pump work chamber.
- the pumping out of the pump work space is ended by opening a first return flow path leading to the suction bore with the aid of a longitudinal groove formed on the pump piston and an inclined lower main control edge of limited circumference.
- the invention is characterized in that recesses are formed on the pump piston and on the pump cylinder u on the catch side, which are delimited in the axial direction by control edges for controlling the multi-stage injection.
- a first stage of injection (“pre-injection”) is ended by the interaction of the control edge of a first recess in the pump cylinder facing away from the pump work space with the control edge of a first recess in the pump piston facing the pump work space by releasing a fluid-conducting second return flow path from the pump work space to the suction bore.
- main injection is regulated by the interaction of the control edge of the first recess in the pump piston facing away from the pump work space with the control edge of the suction bore facing the pump work space by interrupting the second return flow path.
- the fuel injection pump of the present invention thus requires only a suction hole in a structurally simple construction, which serves to supply fuel into the pump work space and to establish a low-pressure path between the suction space and the pump work space. Furthermore, compared to the device shown in GB 893,621, a further design simplification can be achieved in that the beginning of the second stage of the main injection by interaction of the control edge of the first recess in the pump piston facing away from the pump work space with the control edge of the suction bore facing the pump work space by interrupting the second one Return flow path is controlled.
- the suction bore can have a non-round or round cross section.
- the suction bore is equipped with a control edge facing the pump work space and with a control edge facing away from the pump work space.
- control edge facing the pump work space means that semicircle of the the circular control edge surrounding the suction bore, which faces the pump work space
- control edge facing away from the pump work space means that semicircle of the circular control edge surrounding the suction bore, which faces away from the pump work space.
- the invention is advantageously designed such that, when the pump piston is in a position in which the upper main control edge overlaps the control edge of the suction bore facing the pump working space, i. H. a position of the pump piston in which the suction bore has just been closed by the pump piston during its delivery stroke, has a distance, measured in the axial direction, between the control edge of the first recess of the pump piston facing the pump working chamber and the control edge of the first recess of the pump cylinder facing away from the pump working chamber.
- a first useful stroke hm for the pre-injection is defined by the distance mentioned, during which a pre-injection takes place.
- the invention is advantageously designed in such a way that, when the pump piston is in a position in which the control edge of the first recess of the pump piston facing the pump working space covers the control edge of the first recess of the pump cylinder facing away from the pump working space, it measures a distance, measured in the axial direction, between the control edge facing away from the pump working space the first recess of the pump piston and the control edge of the suction bore facing the pump working space.
- This distance defines a first idle stroke h L ⁇ , which corresponds to the time interval between the pre-injection and the main injection.
- the first recess of the pump piston is in the form of a first groove running essentially parallel to the pump piston end face.
- the first groove can advantageously be formed in a rectangular shape.
- the first recess of the pump cylinder and the suction bore are offset relative to one another in the circumferential and axial directions in such a way that the first groove creates a fluid-conducting connection to the suction bore during a delivery stroke of the pump piston, starting from the bottom dead center, which connection during a further delivery stroke of the pump piston merges into a fluid-conducting connection both to the first recess of the pump cylinder and to the suction bore, with a further conveying stroke finally remaining in a fluid-conducting connection to the first recess of the pump cylinder.
- the first recess of the pump cylinder is always in fluid communication with the pump work space.
- Such a functionally characterized arrangement of the first groove, first recess of the pump cylinder and suction bore can advantageously be implemented in such a way that the first recess of the pump cylinder and the suction bore are offset from one another in such a way that their circumferential projections have an overlapping area, whereby the first recess of the pump cylinder in its axial height, viewed in the direction of the delivery stroke, projects beyond the suction bore, while the suction bore in its axial height, viewed in the direction of the delivery stroke, falls below the first recess of the pump cylinder.
- the first recess of the pump cylinder and the suction bore are offset from one another in the circumferential and axial directions in such a way that they are partially arranged at the same axial height, thereby ensuring that a fluid-conducting connection can be created between the suction bore and the first recess of the pump cylinder by means of the first groove.
- the first recess of the pump cylinder and the suction bore are arranged with respect to their axial heights such that the first recess of the pump cylinder, viewed in the direction of the delivery stroke, is higher than the suction bore, while the suction bore, viewed in the direction of the delivery stroke, is lower than the first recess of the pump cylinder.
- the circumferential length of the first groove essentially corresponds to the circumferential length of the projection in the axial direction of the oblique lower main control edge.
- the first recess of the pump cylinder can be in the form of a blind hole with a round, rectangular, square, triangular, parallelogram-like, trapezoidal or arch-shaped cross section.
- the main injection is ended by a cooperation of the control edge of the second recess in the pump piston facing the pump work space with the control edge of the suction bore facing away from the pump work space by releasing a fluid-conducting third return flow path from the pump work space to the suction bore.
- the interaction of the control edge of the second recess in the pump piston facing away from the pump working space with the control edge of a second recess of the pump cylinder facing the pump working space is the beginning a third stage of injection ("post-injection") controlled by interrupting the third return flow path.
- the fuel injection pump according to the invention in addition to a pre-injection and main injection, can also be used to carry out post-injection in a particularly simple manner.
- Post-injection which has so far only been used as standard in very large internal combustion engines equipped with a turbocharger, is particularly advantageous since remaining combustible constituents are burned in the exhaust gas, which in particular leads to a proportion of CO and HC in the exhaust gas is reduced.
- the hot exhaust gases can be used to heat a downstream catalytic converter, which usually only shows satisfactory performance at temperatures above 300-350 ° C. This is particularly important if the internal combustion engine is operated at idle or only at partial load, because then the temperature of the exhaust gases is often too low for the catalytic converter to perform satisfactorily.
- the fuel injection pump according to the invention is advantageously designed such that when the control edge of the first recess of the pump piston facing away from the pump working space and the control edge of the suction bore facing the pump working space overlap, it is a distance in the axial direction between the control edge of the second recess of the pump piston facing the pump working space and that facing away from the pump working space Control edge of the suction hole.
- a second useful stroke h N2 for the main injection is defined by the distance mentioned, during which the main injection takes place.
- the fuel injection pump according to the invention is advantageously designed such that when the control edge of the second recess of the pump piston facing the pump working space and the control edge of the suction bore facing away from the pump working space overlap, it has a distance in the axial direction between the control edge of the second recess of the pump piston facing away from the pump working space and the pump working space facing control edge of the second recess of the pump cylinder.
- a second idle stroke h L2 downstream of the main injection is defined by the distance mentioned.
- the fuel injection pump according to the invention is advantageously designed such that, when the control edge of the second recess of the pump piston facing away from the pump working space and the control edge of the second recess of the pump cylinder facing the pump working space overlap, it has a distance in the axial direction between the control edge of the suction bore facing away from the pump working space and the oblique has lower main control bore.
- a third useful stroke h N3 for the post-injection is defined by the distance mentioned, during which the post-injection takes place.
- the second recess of the pump piston is designed in the form of a second groove which runs essentially parallel to the oblique lower main control edge.
- the second groove can have a rectangular shape.
- the second recess of the pump cylinder and the suction bore are offset from one another in the circumferential and axial directions, such that the second groove successively creates a fluid-conducting connection to the second recess of the pump cylinder during a delivery stroke of the pump piston, which connection in a fluid-conducting connection during a further delivery stroke Connection to both the second recess of the pump cylinder and the suction bore passes over, with a fluid-conducting connection to the suction bore then remaining with a further delivery stroke.
- the second recess of the pump cylinder is always in fluid communication with the pump work space.
- This functional characterization of the relative arrangement between the second.tr recess of the pump cylinder and the suction bore can be designed such that the projection in the direction of the second groove of the second recess of the pump cylinder and the projection in the direction of the second groove of the suction bore have an overlapping area, thereby ensuring is that the second groove can create a fluid-conducting connection between the suction bore and the second recess of the pump cylinder during a delivery stroke.
- the suction bore in its axial height is higher than the projection in the direction of the second groove of the second recess of the pump cylinder, while the axial height of the second recess of the pump cylinder, viewed in the direction of the delivery stroke, is lower than the projection in the direction of the second groove of the suction hole.
- the circumferential length of the second groove essentially corresponds to the circumferential length of the projection in the axial direction of the oblique lower main control edge, so that regulation with regard to post-injection essentially over the entire area of the load regulation is carried out by means of a Rotation of the pump piston relative to the suction hole can take place.
- the second recess of the pump cylinder in the form of a blind hole with a round, rectangular, square schematic, triangular, parallelogram-like, trapezoidal or arched cross-section.
- the upper main control edge has a first bevel in the direction of the longitudinal groove, ie the upper main control edge is beveled against the direction of the conveying stroke.
- a bevel With the aid of such a bevel, regulation of the fuel quantity delivered during a pre-injection can be achieved in a simple manner by rotating the pump piston in the pump cylinder.
- this advantageously makes it possible that, when the pump piston is in a position in which the upper main control edge covers the control edge of the suction bore facing the pump work space, the distance measured in the axial direction between the control edge facing the pump work space and the first recess of the pump piston and that facing away from the pump work space Control edge of the first recess of the pump cylinder becomes zero.
- the first useful stroke hm for the pre-injection becomes zero. If the subsequent idle stroke h L ⁇ is chosen such that an opening of the second return flow path takes place during the idle stroke h L ⁇ , then no main injection takes place either. If, in addition, the subsequent second idle stroke h L2 is selected such that during the second idle stroke h L2 the lower main control edge loops over the suction bore and a fluid-conducting connection between the suction bore and the pump working chamber is established, no post-injection takes place. There is thus a case of zero delivery, which can only be realized in a conventional manner by bringing the longitudinal groove into a juxtaposition with the suction bore.
- a quantity delivery according to a selectable load control position up to zero delivery in standard control.
- the oblique lower control edge can have a second bevel in the direction of the longitudinal groove, adjacent to the longitudinal groove, ie the oblique lower control edge is beveled in the conveying direction.
- zero delivery can be realized in a simple manner by the lower main control edge being looped over the suction bore during the first empty stroke h L ⁇ or during the second empty stroke h L2 and a fluid-conducting connection between the suction bore and the pump working chamber being provided via the longitudinal groove being created.
- both the first bevel and the second bevel are formed in the fuel injection pump according to the invention, a control gap or control quantity step function can be avoided in an extremely advantageous manner.
- FIGS. 1-6 successive phases of the delivery stroke of a pump piston of an embodiment of the fuel injection pump according to the invention with a low control position;
- FIGS. 7-12 successive phases of the delivery stroke of a pump piston of the embodiment shown in FIGS. 1-6. tion form of the fuel injection pump according to the invention at a high control position;
- FIG. 13 shows the embodiment of the fuel injection pump according to the invention shown in FIGS. 1-12 in the control position for a small pilot injection;
- FIG. 14 shows the embodiment of the fuel injection pump according to the invention shown in FIGS. 1-13 in the control position for zero delivery;
- FIG. 15 shows a delivery diagram of the fuel injection pump according to the invention.
- FIGS. 1-6 in which successive phases of the delivery stroke of a pump piston of the illustrated embodiment of the fuel injection pump according to the invention are shown at a low control position.
- a space containing fuel under low pressure is shown in dashed lines, the lines having a wide line spacing (lines run from top left to bottom right), while a space containing fuel under high pressure is shown in dashed lines, with the lines having a small line spacing (Lines run from bottom left to top right).
- FIG. 1 shows, in a schematic cross-sectional representation, only the main elements of a fuel injection pump according to the invention, namely the pump piston 1 and the pump cylinder 2.
- the pump piston 1 and the pump cylinder 2 For the sake of clarity, only a part of the pump piston 1 and the inner wall, which is arranged in the pump cylinder 2 such that it can move axially and rotatably, is shown in the figures of the Pu - penzylinders 2 shown in a superimposed schematic representation.
- the direction of the delivery stroke of the pump piston 1 is indicated by the arrow direction F, while the direction of the suction stroke of the pump piston 1 is indicated by the arrow direction S.
- the pump piston 1 is provided with a pump piston end face 15 delimiting a pump working chamber 16 on the pump side.
- the pump piston end face 15 is surrounded by an upper main control edge 3.
- the pump piston 1 is provided with an oblique lower main control edge 4, a longitudinal groove 5, a first bevel 6 of the upper main control edge 3, a lower bevel 7 of the oblique lower main control edge 4 and a starting slot 8.
- a first groove 9 and a second groove 10 are formed on the circumference of the pump piston 1.
- the first groove 9 which is arranged essentially parallel to the upper main control edge 3 and has a rectangular shape, is provided with a control edge 11 facing the pump work space 16 and with a control edge 12 facing away from the pump work space 16.
- the length in the circumferential direction of the first groove 9 essentially corresponds to the length in the circumferential direction of the projection in the axial direction of the oblique lower main control edge 4.
- the second groove 10 which is arranged essentially parallel to the oblique lower main control edge 4 and is present in a rectangular shape, is provided with a control edge 13 facing the pump work space 16 and with a control edge 14 facing away from the pump work space 16.
- the length in the circumferential direction of the second groove 10 corresponds essentially to that Length in the circumferential direction of the projection in the axial direction of the oblique lower main control edge 4.
- a suction bore 17, a first recess 18 and a second recess 19 are formed on the start side.
- the suction bore 17 is provided with a control edge 20 facing the pump working space 16 and with a control edge 21 facing away from the pump working space 16, the relevant control edges being formed only as parts of the control edge surrounding the suction bore.
- the first recess 18, which is in the form of a blind hole with a rectangular cross section, is provided with a control edge 22 facing the pump working space 16 and with a control edge 23 facing away from the pump working space.
- the second recess 19, which is in the form of a blind hole with an arch-shaped cross section, is provided with a control edge 24 facing the pump working space 16 and with a control edge 25 facing away from the pump working space.
- the first recess 18 of the pump cylinder 2 and the suction bore 17 are offset from one another in the circumferential and axial directions. They are arranged in such a way that their projections have an overlapping area in the circumferential direction, so that they can be connected in a fluid-conducting manner through the first groove 9 in a specific position of the pump piston 1. Furthermore, the axial height of the first recess 18 of the pump cylinder 2, when viewed in the direction of the delivery stroke, is higher than the suction bore 17, while the axial height of the suction bore 17, when viewed in the direction of the delivery stroke, is lower than the first recess 18 of the pump cylinder 2 ,
- the second recess 19 of the pump cylinder 2 and the suction bore 17 are against each other in the circumferential and axial directions added. They are arranged in such a way that the projection in the direction of the second groove 10 of the second recess 19 of the pump cylinder 2 and the projection in the direction of the second groove 10 of the suction bore 17 have an overlapping area, so that they pass through at a specific position of the pump piston 1 the second groove 10 can be fluidly connected.
- the suction bore 17 is in its axial height, viewed in the direction of the delivery stroke, higher than the projection in the direction of the second groove 10 of the second recess 19 of the pump cylinder 2, while the second recess 19 of the pump cylinder 2 in its axial height, in the direction of the Considered delivery strokes, is lower than the projection in the direction of the second groove 10 of the suction bore 17.
- the pump piston 1 is driven in the delivery stroke from its bottom dead center position by an eccentric cam (not shown) of a drive shaft in direction "F", while a return spring (not shown) moves the pump piston 1 in the suction stroke from the top dead center position in the direction "S" ,
- FIG. 1 shows a phase during the delivery stroke of the pump piston 1, in which the connection to the suction chamber is interrupted by means of the upper main control edge 3 surrounding the pump piston end face 15 and the delivery from the pump work chamber 16 is initiated.
- the upper main control edge 3 and the control edge 20 of the suction bore 17 facing the pump working space 16 are in a position overlapping one another.
- First groove 9 and suction bore 17 are connected to one another in a fluid-conducting manner.
- FIGS. 7 to 12 show the successive phases of the delivery stroke of a pump piston in accordance with the embodiment of the fuel injection pump according to the invention shown in FIGS. 1-6 at a high control position.
- the states of the fuel pump shown in FIGS. 7 to 12 each correspond to the states of the fuel injection pump shown in FIGS. 1 to 6.
- FIG. 7 Corresponding to a higher control position, the pump piston 1 in the pump cylinder 2 is rotated in such a way that the suction bore 17 is looped over by a section of the oblique lower main control edge 4 which is further down in the conveying direction compared to the control position shown in FIG. 1.
- FIG. 7 shows a phase during the delivery stroke of the pump piston 1, in which the connection to the suction chamber is interrupted with the aid of the upper main control edge 3 surrounding the pump piston end face 15 and the delivery from the pump work chamber 16 is initiated.
- delivery of fuel from the pump work space is initiated, starting from the pump piston position shown in FIG. 7, since the suction bore 17 is closed by the pump piston 1.
- Fuel is delivered during the useful stroke hm. The state of the fuel injection pump after passing through the useful stroke h is shown in FIG. 8.
- a low-pressure path between the pump work chamber 16 and the suction bore 17 is opened by the second return flow path and the delivery from the pump work chamber 16 is ended.
- the pre-injection is now complete.
- delivery of fuel is initiated from the pump work space (main injection), since the second return flow path is interrupted.
- a delivery of fuel is maintained during the second useful stroke h N2 .
- a low-pressure path between the pump work chamber 16 and the suction bore 17 is opened by the third return flow path and the delivery from the pump work chamber 16 is ended.
- the main injection is now complete (Fig. 10).
- FIG. 13 shows the embodiment of the fuel injection pump according to the invention shown in FIGS. 1-12 at one Control position shown for a small pilot injection.
- the pump piston 1 which is rotatable within the pump cylinder 2, is brought into a position in which the first bevel 6 of the upper main control edge 3 is in a position opposite the suction bore 17.
- the first useful stroke h N ⁇ of the pre-injection is reduced, and consequently the amount of fuel delivered during the first useful stroke h.
- a later closing of the suction bore 17 by the pump piston 1 can be achieved compared to the upper control edge 3 outside the first bevel 6. In this way, the quantity of fuel delivered during the pre-injection can be regulated in terms of quantity by rotating the pump piston 1.
- FIG. 14 shows the embodiment of the fuel injection pump according to the invention shown in FIGS. 1-13 in a control position for zero delivery.
- the pump piston 1 which is rotatable within the pump cylinder 2, is brought into a position in which the first bevel 6 of the upper main control edge 3 is in a juxtaposition to the suction bore 17, the first groove 9 already being covered when the upper one is covered Main control edge 3 with the control edge 20 of the suction bore 17 facing the pump working space 16 by means of the second return flow path in one fluid-conducting connection with the first recess 18 of the pump cylinder.
- the useful stroke h Ni consequently becomes zero. There is no delivery of fuel for a pre-injection.
- a fluid-conducting connection is opened by means of the third return flow path during the first empty stroke h L ⁇ , so that a main injection likewise does not take place.
- the lower oblique main control edge 4 already overlaps the suction bore 17 during the second empty stroke h L2 , so that post-injection does not take place. In this way, zero fuel delivery can be regulated by standard control.
- FIG. 15 shows a delivery diagram of the fuel injection pump according to the invention.
- the delivery diagram shows six individual diagrams A-F, which correspond to different controls of the fuel injection pump.
- the differential injection quantity dQe / d ⁇ versus degree (° KW) of the crankshaft angle ⁇ is plotted in each individual diagram.
- OT denotes the top dead center of the pump piston.
- Individual diagram B corresponds to the case of control with a small pilot injection quantity, which was shown in connection with FIG. 13.
- the beginning of the pre-injection is marked with a, which corresponds to a state of the fuel injection pump in which the suction bore is just closed by the pump piston during the delivery stroke (FIG. 13).
- the end of the pre-injection is marked, which one State of the fuel injection pump corresponds to the second return flow path being opened with a further delivery stroke.
- Individual diagram C corresponds to the case of regulation with a large pre-injection quantity, which was shown in connection with FIGS. 1 to 12.
- the beginning of the pre-injection is identified by a, which corresponds to a state of the fuel injection pump in which the suction bore is just closed by the pump piston during the delivery stroke (FIG. 1, FIG. 7).
- the end of the pre-injection is identified by b, which corresponds to a state of the fuel injection pump in which the second return flow path is opened with a further delivery stroke (FIG. 2, FIG. 8).
- Individual diagram D corresponds to the case of control with a large pre-injection quantity and main injection.
- Letters a and b correspond to the beginning and end of the pre-injection.
- Letters c and d correspond to the beginning and end of the main injection.
- Individual diagram E corresponds to the case of control with a large pre-injection quantity and main injection at part load, which was shown in connection with FIGS. 1 to 6.
- Individual diagram F corresponds to the case of control with a large pre-injection quantity and main injection at full load, which was shown in connection with FIGS. 6 to 12.
- the beginning of the pre-injection is marked with a, which corresponds to a state of the fuel injection pump in which the suction bore has just been closed by the pump piston during the delivery stroke (FIG. 1, FIG. 6).
- the end of the pre-injection is identified by b, which corresponds to a state of the fuel injection pump in which the second return flow path is opened on a further delivery stroke (FIG. 2, FIG. 7).
- the beginning of the main injection is marked with c, which corresponds to a state of the fuel injection pump in which the second return flow path has just been closed (FIGS. 3, 8).
- the end of the main injection is identified by d, which corresponds to a state of the fuel injection pump in which the third return flow path is shortly before the opening (FIG. 4, FIG. 10).
- the start of post-injection is identified by e, which corresponds to a state of the fuel injection pump in which. the third return flow path is just still closed (FIG. 5, FIG. 11).
- the end of the post-injection is identified by f, which corresponds to a state of the fuel injection pump in which the oblique lower main control edge has just not yet grinded over the suction bore (FIG. 6, FIG. 12).
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2006540308A JP2007512461A (ja) | 2003-11-25 | 2004-11-17 | 推進過程制御システムを備えた燃料噴射ポンプ |
EP04803166A EP1687522A1 (de) | 2003-11-25 | 2004-11-17 | Kraftstoffeinspritzpumpe mit f rderverlaufssteurung |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10354921.8 | 2003-11-25 | ||
DE2003154921 DE10354921A1 (de) | 2003-11-25 | 2003-11-25 | Kraftstoffeinspritzpumpe mit Förderverlaufssteuerung |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005052351A1 true WO2005052351A1 (de) | 2005-06-09 |
Family
ID=34625216
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/013044 WO2005052351A1 (de) | 2003-11-25 | 2004-11-17 | Kraftstoffeinspritzpumpe mit förderverlaufssteurung |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1687522A1 (de) |
JP (1) | JP2007512461A (de) |
DE (1) | DE10354921A1 (de) |
WO (1) | WO2005052351A1 (de) |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB893621A (en) | 1959-06-30 | 1962-04-11 | Ceskoslovenske Zd Y Naftovych | Improvements in and relating to fuel injection pumps |
US4824341A (en) * | 1986-11-27 | 1989-04-25 | Daimler-Benz Aktiengesellschaft | Helix-controlled direct fuel injection pump |
DE4103491A1 (de) * | 1991-02-06 | 1992-08-13 | Mtu Friedrichshafen Gmbh | Kraftstoff-einspritzpumpe mit voreinspritzung fuer luftverdichtende brennkraftmaschinen |
JPH07279645A (ja) * | 1994-04-01 | 1995-10-27 | Nippon Soken Inc | 内燃機関の排気微粒子浄化装置 |
-
2003
- 2003-11-25 DE DE2003154921 patent/DE10354921A1/de not_active Withdrawn
-
2004
- 2004-11-17 JP JP2006540308A patent/JP2007512461A/ja active Pending
- 2004-11-17 WO PCT/EP2004/013044 patent/WO2005052351A1/de not_active Application Discontinuation
- 2004-11-17 EP EP04803166A patent/EP1687522A1/de not_active Withdrawn
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB893621A (en) | 1959-06-30 | 1962-04-11 | Ceskoslovenske Zd Y Naftovych | Improvements in and relating to fuel injection pumps |
US4824341A (en) * | 1986-11-27 | 1989-04-25 | Daimler-Benz Aktiengesellschaft | Helix-controlled direct fuel injection pump |
DE4103491A1 (de) * | 1991-02-06 | 1992-08-13 | Mtu Friedrichshafen Gmbh | Kraftstoff-einspritzpumpe mit voreinspritzung fuer luftverdichtende brennkraftmaschinen |
JPH07279645A (ja) * | 1994-04-01 | 1995-10-27 | Nippon Soken Inc | 内燃機関の排気微粒子浄化装置 |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 1996, no. 02 29 February 1996 (1996-02-29) * |
Also Published As
Publication number | Publication date |
---|---|
EP1687522A1 (de) | 2006-08-09 |
JP2007512461A (ja) | 2007-05-17 |
DE10354921A1 (de) | 2005-07-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE3590194C2 (de) | Brennstoff-Einspritzpumpe | |
DE3437053C3 (de) | Diesel-Kraftstoffeinspritzpumpe | |
EP2394049B1 (de) | Brennstoffeinspritzventil für verbrennungskraftmaschinen | |
DE2534295A1 (de) | Maschinenanlage | |
EP0234314A2 (de) | Einspritzventil für Hubkolbenbrennkraftmaschinen | |
DE102005033638A1 (de) | Kraftstoff-Fördereinrichtung, insbesondere für eine Brennkraftmaschine | |
DE2045556B2 (de) | Vorrichtung zur Kraftstoffeinspritzung in die Zylinder einer mit Druckzündung arbeitenden Brennkraftmaschine | |
DE102007000095B4 (de) | Kraftstoffeinspritzelement | |
DE60023168T2 (de) | Verfahren zum vermindern der emissionen in einer brennkraftmaschine | |
DE3809700C2 (de) | ||
DE2904947A1 (de) | Verteiler-einspritzpumpe fuer mit kompressionszuendung arbeitende mehrzylinder-verbrennungsmotoren | |
EP0178487A2 (de) | Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen | |
EP3055549B1 (de) | Kolben-fluidleitung-anordnung, insbesondere steuerkolben-steuerbohrung-anordnung | |
EP0606435B1 (de) | Kraftstoffeinspritzpumpe für brennkraftmaschinen | |
EP1530681B1 (de) | Kraftstoffeinspritzeinrichtung für eine brennkraftmaschine | |
EP0273225B1 (de) | Kraftstoffeinspritzpumpe für Brennkraftmaschinen | |
CH671809A5 (de) | ||
DE2037449C3 (de) | Kraftstoffeinspritzpumpe für Brennkraftmaschinen | |
DE2541363A1 (de) | Verfahren zur regelung der kraftstoffzufuhr zu einer rotationskolben-brennkraftmaschine sowie regeleinrichtung zur durchfuehrung des verfahrens | |
EP1185785B1 (de) | Einspritzsystem | |
DE4310457A1 (de) | Kraftstoffeinspritzpumpe für Brennkraftmaschinen | |
DE102016200487A1 (de) | Brennkraftmaschine | |
DE102007056418A1 (de) | Einspritzanlage für eine Brennkraftmaschine | |
WO2005052351A1 (de) | Kraftstoffeinspritzpumpe mit förderverlaufssteurung | |
DE102013108868B4 (de) | Brennkraftmaschine mit Fluidadditionsabschnitt zur Hinzufügung eines nicht-brennbaren Fluids zu einem Abgas |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2004803166 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 200480031640.3 Country of ref document: CN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2006540308 Country of ref document: JP |
|
WWP | Wipo information: published in national office |
Ref document number: 2004803166 Country of ref document: EP |
|
WWW | Wipo information: withdrawn in national office |
Ref document number: 2004803166 Country of ref document: EP |