EP2665919A1 - Kraftstofffördervorrichtung für eine verbrennungskraftmaschine - Google Patents
Kraftstofffördervorrichtung für eine verbrennungskraftmaschineInfo
- Publication number
- EP2665919A1 EP2665919A1 EP11802655.8A EP11802655A EP2665919A1 EP 2665919 A1 EP2665919 A1 EP 2665919A1 EP 11802655 A EP11802655 A EP 11802655A EP 2665919 A1 EP2665919 A1 EP 2665919A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- fuel
- delivery device
- line
- valve
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 290
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 23
- 239000002828 fuel tank Substances 0.000 claims abstract description 10
- 238000001914 filtration Methods 0.000 claims abstract description 8
- 239000002245 particle Substances 0.000 claims abstract description 8
- 238000002347 injection Methods 0.000 claims description 19
- 239000007924 injection Substances 0.000 claims description 19
- 230000000903 blocking effect Effects 0.000 claims description 18
- 239000012530 fluid Substances 0.000 claims description 9
- 238000011144 upstream manufacturing Methods 0.000 claims description 5
- 238000010926 purge Methods 0.000 claims description 3
- 239000003502 gasoline Substances 0.000 claims description 2
- 238000003860 storage Methods 0.000 description 28
- 238000004146 energy storage Methods 0.000 description 7
- 238000010586 diagram Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 5
- 238000007789 sealing Methods 0.000 description 5
- 238000004140 cleaning Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- 238000011109 contamination Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 239000011324 bead Substances 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 230000005672 electromagnetic field Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000005429 filling process Methods 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 210000004907 gland Anatomy 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000014759 maintenance of location Effects 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000011045 prefiltration Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000002940 repellent Effects 0.000 description 1
- 239000005871 repellent Substances 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0047—Layout or arrangement of systems for feeding fuel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/22—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system
- F02M37/32—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system characterised by filters or filter arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
- F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
- F02M37/0023—Valves in the fuel supply and return system
Definitions
- the invention relates to a fuel delivery device for an internal combustion engine, with at least one fuel tank from which a fuel pump via a fuel line promotes fuel to a fuel consumer, wherein at least one fuel filter is provided for filtering the fuel.
- fuel injectors are pump-nozzle devices or pump-line devices such as storage-injection systems (common-rail) is used.
- common-rai l injection systems allow the injection pressure to adapt to the respective load and the speed of the respective internal combustion engine.
- the highest possible injection pressure is desired.
- the fuel for such fuel injectors is conveyed in a conventional manner with fuel delivery devices from a fuel tank by means of a fuel pump via a fuel line to a high-pressure fuel source, usually a high-pressure fuel pump.
- the high-pressure fuel source can also be formed as a pressure booster.
- the high-pressure fuel source in turn in common-rail injectors, a high-pressure fuel line or high-pressure distributor strip is used, at which fuel injectors are fluidically connected, at least in the number of combustion chambers to be supplied with fuel.
- Fuel injectors of such fuel injectors which have high-pressure accumulator lines such as a common-rail line, have very small throttles and valve port cross-sections. For a perfect permanent function of the fuel injectors therefore the filtering of the fuel is indispensable.
- DE 199 10 970 A1 shows and describes a fuel injection device which has a pressure booster unit between a pressure storage space and a nozzle chamber, whose pressure chamber is connected via a pressure line to the nozzle chamber of a fuel injector. Furthermore, a bypass line connected to the pressure storage space is provided. The bypass line is usable for pressure injection of the fuel and arranged in parallel to the pressure chamber, so that the bypass line is held continuously regardless of the movement and position of a valve element of the pressure booster unit.
- DE 102 47 210 A1 shows a fuel injection device for internal combustion engines with a, acted upon by a high-pressure fuel source fuel injector, wherein the fuel high pressure source comprises a pressure booster containing a movable piston-shaped transmission element, which connects a connectable to the high-pressure source via a high-pressure line working space of a separates the fuel injector acting high pressure space.
- the fuel high pressure source comprises a pressure booster containing a movable piston-shaped transmission element, which connects a connectable to the high-pressure source via a high-pressure line working space of a separates the fuel injector acting high pressure space.
- EP 1 387 079 A1 shows and describes a common-rail fuel injection system with a high-pressure pump, which supplies the rail system with fuel via a flow rate control, to which fuel injectors for fuel injection of each cylinder of an internal combustion engine are connected.
- the high-pressure pump is supplied with fuel via a low-pressure feed pump, with the low-pressure feed pump drawing in fuel from a tank and passing it via a fuel filter to the high-pressure pump.
- the operating pressure in the rail system is regulated by means of an electronic control unit.
- DE 103 36 223 A1 describes a fuel filter which is pressed into a mounting hole of a fuel injector.
- the fuel filter has an inlet portion at an open end of a fuel inlet side and a filter portion having a number of openings.
- a bottom of the filter portion is hemispherical-shaped, so that a flow area formed between an outer surface of the hemispherical bottom and the circular inner surface of the installation hole is progressively expanded to reduce the pressure loss rate.
- a fuel filter very thin foreign matter and needle-like foreign matter to be prevented from the passage to the relevant fuel injector.
- such a fuel filter on a sufficient flow area, so that in addition to a high retention capacity, a very low pressure loss is effected on the fuel filter.
- the known fuel delivery devices in particular for fuel injection devices of internal combustion engines, have a design-related operating time, which is in particular determined by the type of fuel filter used.
- the present invention seeks to provide a fuel delivery device whose operating time is increased compared to known fuel delivery devices.
- the fuel delivery device for an internal combustion engine provides a means for forming a backflow of fuel at least through the at least one fuel filter, wherein the return flow of fuel through the fuel filter, in particular for the separation of particles which have been deposited on the fuel filter used.
- the return flow through the fuel filter can also cause the possibly occurring short-term surface deformations of its filter material to be reversed during operation of the fuel filter.
- the device for forming a return flow may in this case have a pressure vessel which can temporarily apply a fuel volume flow against the main conveying direction of the fuel pump to the fuel filter.
- the fuel filter is in this case flowed through counter to its main flow direction, so that particles deposited on its surface and in its filter material are released and deposited in the fuel container or another container which is not flowed through by fuel during operation of the fuel delivery device. can be directed. Furthermore, it is possible for me that releasing dirt settles in this purpose fluidly favorable areas of the fuel filter itself.
- the filter life of the fuel filter is increased by this measure according to the invention, which also ensures the functi- onLink and longevity for a common rail system.
- the means for generating the backflow comprises a pressure vessel receiving fuel under a bias pressure in a charge cycle from the fuel injection device and delivering fuel to the fuel line to form the return flow in a discharge cycle.
- the arrangement is preferably made such that the pressure vessel is formed by a hydraulic accumulator, the working space during the discharge cycle to form the return flow via a purge line to a port of the fuel line is connected, which is located between the filter and the fuel pump.
- the device which generates the return flow has a switching valve via which the working space of the hydraulic accumulator can be selectively connected to the fuel line and to the flushing line.
- the Heidelbergi l has only two useful connections and preferably two switching positions in a first particularly simple design.
- fuel is directed against the main conveying direction in the fuel line to the fuel filter to be cleaned for the purpose of cleaning the fuel filter.
- the return flow is preferably generated in the pressureless state of the fuel line from the device for forming a return flow.
- the switching valve is formed with a valve element in which a switching position is realized by a pilot-operated check valve in the valve element, a blocking function of the pressure vessel to the fuel line.
- the pilot-operated check valve can be flowed through by fuel, so that a working chamber of the pressure vessel can be refilled with fuel. It may also be expedient to provide a blocking block in the valve element of the respective switching valve instead of the pilot-operated check valve. In this case, the recharging function of the pressure vessel with fuel is ensured by an inserted into the supply line to the pressure vessel unlockable Rutschventi l.
- the switching valve may also be advantageous to design the switching valve as a 3/2-way valve, wherein a first useful port of the 3/2-way valve to the pressure vessel, a second Nutzan gleich to the fuel line upstream of a second fuel filter and a third Nutzan gleich upstream of the first fuel filter connected to the fuel line.
- a first useful port of the 3/2-way valve to the pressure vessel a second Nutzan gleich to the fuel line upstream of a second fuel filter and a third Nutzan gleich upstream of the first fuel filter connected to the fuel line.
- the blocking Stel development of the valve element thus ensures a rechargeability of the working space of the pressure vessel with fuel. It may also be advantageous to block the first and second Nutzanschl uss by a blocking block against each other in a blocking position of the valve element of the 3/2-way valve.
- the design of the switching valve in the manner of a 3/3-way valve allows in a particularly space-saving manner the functions of unloading the pressure vessel and generating a return flow, blocking position in the main operation of the fuel delivery device and recharging the working chamber of the pressure vessel with fuel.
- the fluid connection in particular the fuel line upstream of the second fuel filter to produce the pressure vessel in a position is, is locked here.
- the pressure vessel of the device can be formed both as a diaphragm accumulator, as a piston accumulator or as a bellows accumulator or from a combination of said accumulators. It is understood that in principle also other fuel sources, which are able to apply a suitable fuel pressure for generating a return flow to the relevant fuel filter, can be applied.
- the fuel delivery device according to the invention is particularly suitable for conveying fuel in a fuel injection device of a diesel or gasoline engine. It may be advantageous, the pressure vessel, in particular the working space of a piston or bellows, from a fluid pressure in a fuel return line of fuel injectors of the fuels! n-injection device to apply.
- FIG. 1 shows the fuel delivery device according to the invention with means for forming a backflow of fuel through two fuel filters; another embodiment of a schematic circuit diagram of a fuel delivery device constructed comparable as shown in Figure 1; another embodiment of a schematic circuit diagram of a fuel delivery device constructed comparable as shown in Figure 1; another embodiment of a schematic diagram of a fuel delivery device with a 3/3-way valve in a device for forming a backflow of fuel through a fuel filter of the fuel delivery device; a longitudinal section through an embodiment of a piston accumulator for the means for forming a return flow; a longitudinal section through a further, second embodiment of a piston accumulator for the means for forming a return flow; a longitudinal section through a further, third embodiment of a piston accumulator for the means for forming a return flow; and a longitudinal section through a further, fourth embodiment of a piston accumulator for the means for forming a
- FIG. 1 shows a schematic circuit diagram of a fuel delivery device for delivering fuel from a diesel fuel combustion engine from a fuel tank 2 via a fuel line 1 to fuel injectors 30 at the respective combustion chambers of the diesel internal combustion engine.
- the fuel delivery device shown has a low-pressure side and a high-pressure side, wherein on its low-pressure side fuel is conveyed by a fuel pump 3 via the fuel line 1 from the fuel tank 2.
- the fuel pump 3 is shown as a fluid pump with a constant delivery volume.
- the fuel pump 3 serves to convey fuel via a section 4 of the fuel line 1 to a high-pressure pump with constant displacement volume formed high-pressure fuel source 6.
- a fuel filter 1 2 introduced for pre-filtration of the fuel.
- a second fuel filter 7 is introduced between the fuel pump 3 and the high-pressure fuel source 6.
- this fuel filter 7 is used for ultrafine filtration of the fuel prior to its entry into the high-pressure fuel source 6, which may also be designed as a pressure booster.
- Both fuel filters 12, 7 are capable of filtering both the finest, in the assembly of the fuel delivery device in the relevant fluid-carrying compounds particles 10 as well as suspended solids and the like, which are constantly tracked in a refueling operation of the fuel tank 2, from the fuel. 1 to 4 for fuel supply to a fuel injector 27.
- the fuel injector 27 shown is formed as a common rail system (CR).
- CR common rail system
- Such accumulator injection systems or common rail systems advantageously make it possible to adapt the injection pressure of fuel into respective combustion chambers of the internal combustion engine at load and rotational speeds of the internal combustion engine.
- the fuel injector 27 or the common rail system is simplified with a high-pressure manifold 32, to which the four fuel injectors 30 are fluidly connected, shown.
- Such fuel injectors 30 have, inter alia, inlet throttles and valve opening cross sections, which are very small, so that a fine filtration of the fuel with the aid of a fuel filter 7 is necessary for proper functioning of such fuel injectors to smallest contamination particles, for example, during assembly the system parts can enter the system to keep away from the sensitive components, in particular from the fuel injectors 30.
- the fuel injectors 30 shown also each have a return line, which is connected in a fluid-carrying manner to a fuel return line 29 of the fuel delivery device 1, so that fuel can return to the fuel tank 2 via the fuel return line 29.
- a device 8 for forming a return flow of fuel is provided at least by the fuel filter 7.
- the device 8 is essentially formed in the exemplary embodiments shown in FIGS. 1 to 3 from a pressure vessel 9 and a switching valve 1 1.
- the pressure vessel 9 is in all embodiments from a hydraulic accumulator whose gas side 1 3 containing a working gas (N 2) is separated from a fluid-side working space 28 by a movable separating element.
- the switching valve 1 1 is formed in the embodiments of FIGS. 1 to 3 as a 3/2-way valve 18. In Fig.
- the pressure vessel 9 is shown as a diaphragm accumulator 24 for storing fuel in the working space 28.
- the accumulator pressure in the working space 28 is merely approx. 5 bar by way of example.
- the pressure vessel 9 is fluidly connected via a first service port 19 to the switching valve 1 1.
- a second service port 20 on the switching valve 1 1 is in turn fluidly connected to the fuel line 1, more specifically connected to a connection point 33 on the section 4 of the fuel line 1.
- the 3/2-way valve 18 has, in addition to the first pay port 19, the second user port 20 nor a third Nutzan gleich 21, which has a fluid-carrying connection 39 between the working space 28 and a connection point 40 between the fuel filter 12 and the fuel pump 3 in the Fuel line 1 is arranged allows.
- the valve element has the unlockable non-return valve 15 (shown in FIG. 1 between the first and second working ports 19, 20).
- the 3/2-way valve 18 has in FIGS. 1 to 3 shown embodiments, in principle, two switching positions, wherein a valve element 14 of the 3/2-way valve s 18 in a blocking position with respect to the fluidic connection of the Nutzan say 19, 20 is shown.
- the blocking position of the valve element 14 shown is generated by a spring element 34, which biases the valve element 14.
- the 3/2-way valve 18 is shown as an electrically actuated valve, wherein in an energized switching position of the first Nutzan gleich 19 fluidly connected to the second Nutzan gleich 20 and third Nutzan gleich 21, so that at the same time fuel from the working space 28 of the fuel delivery device in an operating pause Diaphragm accumulator 24 both in the section 4 of the fuel line.
- the fuel delivery device shown in Fig. 1 comprises a valve element 14 of the switching valve 1 1, which includes a pilot-operated check valve 1 5.
- the lockable check valve 1 5 assumes the same function "refilling the working chamber 28 of the pressure vessel 9" as the pilot-operated check valve 36 in the bypass line 35 in Fig. 2.
- the unlockable check valve 15 in the valve element 14 is in a closed position, see that fuel from the working space 28 can not get into the section 4 of the fuel line 1 and through the fuel filter 7.
- the pressure vessel 9 is formed as a so-called Belg Eaton 26, wherein a bellows, in particular a Metallblag 37, serves as a separating element between the fuel in the working space 28 and a spring chamber 38.
- a bellows in particular a Metallblag 37
- Such hydraulic accumulator with serving as a movable separating element metal bellows are known in principle and disclosed by way of example in a prior application of the applicant (DE 10 2008 061 221 AI).
- the same reference numerals apply as in the preceding figure.
- a blocking block 16 between the first and second user port 19, 20 is provided in the embodiment of FIG. 3.
- the device 8 has a designed as a 3/3-way valve 22 switching valve 1 1.
- the 3/3-way valve 22 is disposed between the first Nutzan gleich 19 and the second and third Nutzan gleich 20, 21, and between the pressure vessel 9 and the fuel line 1 and controls for the purpose of generating a return flow and for the purpose of recharging the working space 28 of Pressure vessel 9, the respective fuel flows.
- the pressure vessel 9 is shown as a piston accumulator 25 for storing fuel in the working space 28.
- the 3/3-way valve 22 is exclusively electrically operated, not spring-centered, and in particular has a third switching position, in which the valve element 23 allows a fluidic connection between the second user port 20 and the first user port 19, wherein the third user port 21 is locked , In this switching position recharging the Härau ms 28 is possible with fuel.
- the recharging of the working space 28 of the illustrated pressure vessel 9 in FIGS. 1 to 4 takes place during normal operation of the fuel delivery device when the internal combustion engine is in operation.
- the operation of the device 8 for the purpose of generating a return flow of fuel to both fuel filters 12, 7 is preferably carried out during a break in operation of the internal combustion engine.
- a pressure vessel 9 for the pulse-like release of a storeable in a working space 28 fuel quantity 41 is shown.
- a cylindrical storage housing 42 of the pressure vessel 9 has a first energy store 43, which is designed as a cylindrical compression spring.
- the energy store 43 serves to load a piston Bens 44 with a predetermined compressive force, the pressure force is sufficient to pulse the piston 44 from a locked position to a position in which the amount of fuel 41 is pushed out of the storage housing 42, pulse.
- the piston 44 is held after the filling of the working space 28 by a locking device 45, which holds the piston 44 with latching means 46, in the shown biased position of FIG.
- an actuating device 47 is provided, with which the locking means 46 can be brought into a position in which the latching at the end portion 48 of the piston 44 is released.
- the end portion 48 of the piston 44 in which engage the locking means 46 in the latched position of the piston 44, the stored fuel amount 41 is arranged opposite, whereby a maximum travel of the piston 44 in the storage housing 42 is ermögl light.
- the locking means 46 are held in the embodiment shown in FIG. 5 in an axially unchangeable position on a holding device 49, which is designed as a hollow cylinder 50.
- a holding device 49 which is designed as a hollow cylinder 50.
- this piston 44 along its inner side 51 locking surfaces 52 which are engageable in latching engagement with the locking means 46.
- the actuating device 47 shown in Figure 5 is essentially formed of a multi-membered kern actuating plunger 53 which is axially guided by a magnet system 54, in the holding device 49 is axially movable.
- the actuating plunger 53 is shown in an initial state in which it is held by a second, as helical compression spring gebi ldeten energy storage 55, wherein the locking means 46 are out of engagement with the end portion 48 of the piston 44 and the second energy storage 55 a maximum length.
- the latching surfaces 52 are arranged along the cylindrical inner circumference 56 of the end region 48 of the piston 44 and are formed in particular by a linear transition 57 between cylindrical guide surfaces 58 of the piston 44 and a latching chamber 59 which widens in diameter ,
- the inner periphery 56 and said inner side 51 form parts of the inner wall of the piston 44 facing the latching means 46.
- the latching chamber 59 is in turn axially bounded by the bottom of the piston 44, so that overall a maximum possible travel of the piston 44 is achieved before the latching takes place.
- the piston 44 is in the locked position shown in Figure 5 with its, the fuel quantity 41 facing away from the free end of a stop 60 on the outer circumference of the holding device 49 and is held axially immovably between the locking means 46 and the stopper 60.
- the locking means 46 are formed in the illustrated embodiment as rolling elements 61, in particular as locking balls 62, which are held in their axial position by cage-like recesses 63 in an end region of the holding device 49.
- the locking balls 62 are either supported radially on the latching surfaces 52, which are designed as an approximately 45-degree inclined surfaces of the holding device 49 repellent, on which the latching chamber 59 forming end portion 48 of the piston 44.
- the locking balls 62 may also be supported on the inner side 51 of the piston 44 on the cylindrical guide surfaces 58 of the piston 44 itself. Seen radially towards the actuating tappet 53, the detent balls 62 are supported on a cylindrical, thickened control part 64 of the actuating tappet 53.
- the control part 64 has a circumferential groove 65, the edges of which form latching or oblique surfaces for changing the radial position of the latching balls 62.
- the oblique surfaces or flanks of the circumferential groove 65 in the control part 64 are shaped such that in the case of a radial displacement movement of the control part 64 to the cage-like recesses 63 in the holding device 49 the detent balls 62 are pressed radially outward, but remain in the recesses 63 as soon as the detent surfaces 52 in the detent chamber 59 of the piston 44 reach the vicinity of the recess 63 or are congruent with the cage-like recesses 63.
- the holding device 49 is formed as Zyl indians, the egg nen approximately half as large outer diameter, as the storage housing 42 itself.
- the piston 44 is on its, the working space 28 side facing away formed as a cylindrical sleeve 66, wherein the sleeve 66 is integrally connected to the piston 44.
- the sleeve 66 slides along the outer periphery of the retainer 49.
- the retainer 49 is shown integrally formed with a lid 67 for ease of illustration, which closes the accumulator housing 42 toward the magnet system 54 (see FIG.
- the lid 67 is crimped to the wall 68 of the accumulator housing 42 with a radial circumferential bead 69 directed towards the wall 68 mating with the lid 67 into the wall 68, thus providing an additional positive connection between the lid 67 and the wall 68 trains.
- the cover 67 has a cylindrical receptacle 70 for centering the electromagnet 71 of the magnet system 54 flanged to the cover 67.
- the actuating tappet 53 is connected to an armature of the magnet system 54 (not shown in any more detail) via a stub screw 72, so that a fine adjustment of the position of the actuating tappet 53 relative to the retaining device 49 can take place.
- the Stel lschraube 72 is determined by a nut 73 in a conventional manner in contact with the actuating plunger 53 konternd.
- the solenoid 71 of the magnet system 54 is shown in a de-energized state and the second energy storage 55 assumes its extended position, in which it lêttei 64 to an axial stop 74 on the inner circumference of the holding device 49 pulls.
- the stop 74 is arranged at the free end of the holding device 49.
- the second energy store 55 which is likewise designed as a cylindrical compression spring, is arranged in a cylindrical spring space 75 between the actuating tappet 53 and the holding device 49 and is supported at a point of the actuating tappet 53 and on an annular stop 76 of the holding device 49. If the actuating tappet 53, viewed in plan view in FIG.
- the piston 44 is released and, under the action of the pressure force of the first energy accumulator 43, is moved in a pulse-like manner in the viewing direction of FIGS. 5 and 6 to the right up to its abutment against a second cover 78 of the accumulator housing 42.
- the first energy storage 43 is supported on the cover 67 and on the rear side of the piston 44, which faces away from the working space 28.
- the total amount of fuel 41 stored in the storage housing 42 or in the working space 28 is discharged abruptly from the storage housing 42 at the corresponding switching position of the switching valve 1 1 and fed into the section of the fuel I 1 and the fluid-conducting connection 39 for the return flow ,
- FIG. 6 shows a longitudinal section through a basically similar pressure vessel 9 for impulsively releasing a quantity of fuel 41 that can be stored in its storage housing 42, but its holding device 49, its locking device 45 and its actuating device 47 are of the embodiment according to FIG Fig.5 separates.
- the actuating tappet 53 has an approximately constant outer diameter over its length and is formed in one piece with its end-side control part 64.
- a circumferential groove 65 in the control part 64 has a greater width than in the embodiment according to FIG.
- the locking means 46 are formed as a rail profile in the form of a profile, designed in the manner of rocker arms locking cam 79.
- the locking cams 79 have a first free end 80 with which they are held pivotably in a receptacle formed as a radially outer circumferential groove at the end of the holding device 49. With their respective other end 81, the locking cams 79, of which only two are shown by a plurality, guided in the circumferential groove 65 in the control part 64 engaging.
- the engaging in the circumferential groove 65 locking lugs 82 of the locking cam 79 are constructed asymmetrically and have smaller locking lugs 83 in cross-section, which are directed radially outward, with which the locking cam 79 can slide along the inside of the piston 44.
- FIG. 6 shows a piston position of the piston 44, which corresponds to the maximum amount of fuel 41 to be received in the storage housing 42, wherein the actuating plunger 53, caused by an expansion of the second energy storage 55, a different process position related to the magnet system 54 occupies.
- the actuating plunger 53 By this movement of the actuating plunger 53, the latching nose 82, which faces the piston 44, displaced from its, lying in the circumferential groove 65 position and moved radially outwardly to the latching surfaces also formed as inclined surfaces in the latching chamber 59.
- There is a latching of the piston 44 thereby.
- the supply and removal of the fuel quantity 41 takes place via the first service port 19 on the switching valve 11.
- FIG. 7 shows in a longitudinal section a pressure vessel 9 for pulse-like release of a quantity of fuel 41 that can be stored in a storage housing 42.
- the cylindrical storage case 42 has a first one Energy storage 43, which is designed as a cylindrical compression spring.
- the first energy storage 43 serves to load a piston 44 with a pressure force which is sufficient to bring the piston 44 from a locked position to a position in which the amount of fuel 41 is expelled from the storage housing 42 in a pulse-like manner.
- a valve device 84 controls the fuel flow between the accumulator housing 42 and the switching valve 1 1, which is fluidly connected to an output of the valve device 84.
- the valve device 84 is designed as a seat valve, wherein a provided with a flat sealing surface valve piston 85 comes to rest on a conically widening to the sealing surface of the valve piston 85 valve seat V in the closed state of the seat valve.
- a check valve 86 is installed, which is installed blocking in the filling direction of the storage housing 42.
- the check valve 86 allows a flow in the sense of outflow of the amount of fuel 41 from the storage housing 42 and thus provides an additional opening cross-section to the released from the valve piston 85 opening cross-section. This is made possible by the fact that the valve piston 85, which controls a valve seat, has a control section 87 in the manner of a valve slide.
- the control section 87 blocks in a closed position of the poppet valve a fluid-carrying connection of the accumulator housing 42 with the check valve 86 and opens the fluid-carrying connection at an open position of the valve piston 85, wherein in a corresponding switching position of the valve element 14 of the switching valve 1 1 is a backflow of fuel can take place via the section 4 of the fuel line 1 and the fluid-carrying connection 39 to the fuel filters 12, 7 (see Fig. 1 to 4).
- the valve device 84 is designed as a screw-in valve and can be detached as a functional unit in a cover 78 of the reservoir. chergebliuses 42 arranged.
- the longitudinal axis of the valve device 84 is perpendicular to the longitudinal axis 77 of the storage housing 42 and cuts them.
- the lid 78 is U-shaped in cross-section and screwed with an annular rim over about 1/5 of the length of the storage housing 42 by a thread on the outside of the storage housing 42.
- a per se known, designed as an O-ring sealing element 88 is mounted between the lid 78 and the storage housing 42.
- the storage housing 42 or the working chamber 28 is fed by the fuel pump 3 with fuel, the piston 44 against the restoring force of the The seat valve is closed after the filling process of the accumulator housing 42 and thus holds the piston 44 in a prestressed position as a hydraulic locking device.
- FIG. 8 shows in a longitudinal section a pressure vessel 9 for pulse-like release of a quantity of fuel 41 that can be stored in a storage housing 42.
- the cylindrical storage housing 42 of the pressure vessel 9 has a first energy store 43, which is designed as a cylindrical pressure spring.
- the energy accumulator 43 serves to urge the piston 44 with a pressing force sufficient to move the piston 44 from its biased position as shown in FIG. 8 to a position in which the fuel amount 41 is exhausted from the accumulator housing 42 method.
- the amount of fuel 41 is introduced in the position shown in Figure 8 of the piston 44 by the fuel pump 3 in the storage housing 42 under pressure (see Fig.1).
- the piston 44 is held after the filling by a locking device 45 in the shown biased position.
- the locking device 45 is formed from a piston-cylinder arrangement 89.
- the piston-cylinder arrangement 89 includes a working piston 90 fixedly connected to the storage housing 42 in the embodiment shown in FIG. 8.
- the working piston 90 is arranged as a substantially cylindrical sleeve with an approximately half-axial length at its circumference, annular elevation 91 formed.
- a cylinder housing 92 is arranged, which is formed by a shaft 93 on the piston 44.
- the working piston 90 has an outer diameter Da which corresponds to that of the inner diameter Di of the shaft 93 in a stuffing box region S, plus a predefinable tolerance dimension.
- the annular elevation 91 which essentially forms the working piston 90, forming a gap 94, is spaced from the cylinder housing 92 and forms a certain separation between a first working chamber 95 and a second working chamber 96 between the working piston 90 and the cylinder housing 92 out.
- the gap 94 is formed as an annular gap.
- the annular elevation 91 forms, together with the gap 94, a valve 97 for an electrorheological fluid 98 filled in the two working chambers 95, 96.
- an end remote from the piston 44 extends beyond the annular elevation 91 protruding electromagnetic coil 99 is arranged, the voltage supply through an axial opening 100 in a, the storage housing 42 end closing lid 67.
- first working chamber 95 is not in the direction of second working chamber 96 can be flowed over.
- the first working chamber 95 which extends axially from one, the gland portion S forming sealing means 101 to the annular projection 91 on the working piston 90 remains completely filled with the electrorheological fluid 98, wherein tensile forces be transmitted from the sealing device 101 via the shaft 93 to the piston 44 and hold the piston 44 in its position.
- the locking device 45 is formed in this way by the piston-cylinder arrangement and the electrorheological fluid 98.
- the coil 99 forms, together with a control unit which drives the latter and is supplied with electrical voltage, the actuating device 47 for the pressure vessel 9.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102011009035A DE102011009035A1 (de) | 2011-01-21 | 2011-01-21 | Kraftstofffördervorrichtung für eine Verbrennungskraftmaschine |
PCT/EP2011/006509 WO2012097852A1 (de) | 2011-01-21 | 2011-12-22 | Kraftstofffördervorrichtung für eine verbrennungskraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2665919A1 true EP2665919A1 (de) | 2013-11-27 |
EP2665919B1 EP2665919B1 (de) | 2018-02-21 |
Family
ID=45422102
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP11802655.8A Active EP2665919B1 (de) | 2011-01-21 | 2011-12-22 | Kraftstofffördervorrichtung für eine verbrennungskraftmaschine |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2665919B1 (de) |
DE (1) | DE102011009035A1 (de) |
WO (1) | WO2012097852A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017007603A1 (de) | 2017-08-11 | 2019-02-14 | Hydac Fluidcarecenter Gmbh | Fördervorrichtung für den Kraftstoff einer Verbrennungs-Kraftmaschine |
CN115445280B (zh) * | 2021-07-13 | 2024-03-12 | 青岛经济技术开发区海尔热水器有限公司 | 一种多档位切换的净水装置及热水器 |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5960775A (en) * | 1997-12-08 | 1999-10-05 | Walbro Corporation | Filtered fuel pump module |
DE19910970A1 (de) | 1999-03-12 | 2000-09-28 | Bosch Gmbh Robert | Kraftstoffeinspritzeinrichtung |
EP1409109A4 (de) * | 2001-07-20 | 2005-01-12 | Bang Gyoon Jung | Rückspülventil und dieses enthaltende filtriervorrichtung |
ITBO20020498A1 (it) | 2002-07-30 | 2004-01-30 | Magneti Marelli Powertrain Spa | Impianto di iniezione di carburante di tipo common rail con pompa a portata variabile |
JP3841054B2 (ja) | 2002-08-08 | 2006-11-01 | 株式会社デンソー | フィルタおよびそれを用いた燃料噴射装置 |
DE10247210A1 (de) | 2002-10-10 | 2004-04-22 | Robert Bosch Gmbh | Filteranordnung für Kraftstoffeinspritzsysteme |
DE102004053671A1 (de) * | 2004-11-03 | 2006-05-04 | Knoll Maschinenbau Gmbh | Vorrichtung zur Trennung eines Phasengemisches |
JP5024213B2 (ja) * | 2008-07-18 | 2012-09-12 | コベルコ建機株式会社 | フィルタ洗浄装置 |
DE102008061221A1 (de) | 2008-12-09 | 2010-06-10 | Hydac Technology Gmbh | Hydrospeicher, insbesondere Balgspeicher |
-
2011
- 2011-01-21 DE DE102011009035A patent/DE102011009035A1/de not_active Withdrawn
- 2011-12-22 EP EP11802655.8A patent/EP2665919B1/de active Active
- 2011-12-22 WO PCT/EP2011/006509 patent/WO2012097852A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2012097852A1 * |
Also Published As
Publication number | Publication date |
---|---|
EP2665919B1 (de) | 2018-02-21 |
DE102011009035A1 (de) | 2012-07-26 |
WO2012097852A1 (de) | 2012-07-26 |
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