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
  • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
  • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
  • F02M55/008—Arrangement of fuel passages inside of injectors
• • 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
  • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

• Injector for injecting high-pressure fuel into the combustion chamber of an internal combustion engine
• injectors for injecting high-pressure fuel into a combustion chamber of an internal combustion engine in injectors for injecting high-pressure fuel into a combustion chamber of an internal combustion engine, as are known from the field of storage injection systems, the control of the injection process in dependence on the position of a control valve, which is associated with a control chamber of a valve spool.
• the control chamber is in this case connected via an inlet bore in terms of flow with a high-pressure line via which the injector is supplied with the high-pressure fuel.
• the control chamber of the valve control piston is connected via an outflow bore to a pressure equalization chamber, the drainage bore being closed by the pressure-compensating control valve.
• the high-pressure fuel flows through the drain hole from the control chamber into the pressure compensation chamber of the injector, whereby the valve spool is released.
• the release of the valve control piston opens a nozzle needle valve, via which the fuel is injected into the combustion chamber of the internal combustion engine.
• the dynamic opening and closing behavior of the nozzle needle valve which is dependent on the change in the control volume in the control chamber of the valve spool, can be determined by the design of an inlet throttle provided in the inlet bore and an outlet bore provided in the drain hole.
• the high pressure fuel flows from the control chamber at a high flow rate through the drain hole in the direction of the pressure equalization chamber of the injector, resulting in a reduction of the cross section in the region of the drain hole and the drain throttle local changes in the fuel pressure. Since in storage injection systems of the fuel with a pressure of about 100 MPa or 1000 bar is applied, it may come due to the highly dynamic fluid movement to a local pressure drop, which leads to the local formation of vapor bubbles. In the subsequent cross-sectional reduction Pressure phases implode these vapor bubbles, which is also referred to as cavitation.
• the resulting high local energy density leads over time to a hollowing on the surface of the delimiting wall and thus to an undesired removal of material as well as a wear on the valve seat of the control valve.
• the surface on the valve seat and in the seating area of the valve body is thus damaged, which can result in a leakage of the control valve and thus an injector malfunction.
• the invention is therefore based on the object to provide an injector for the injection of high-pressure fuel into the combustion chamber of an internal combustion engine, in which caused by Kavitationserosion damage to the valve seat of a pressure-compensating control valve, which closes the drain hole of a control chamber is avoided.
• the injector for injecting high-pressure fuel into the combustion chamber of an internal combustion engine comprises an at least approximately rotationally symmetrical control chamber to which a valve control piston is assigned.
• the control chamber is connected via an inlet bore hydraulically connected to the high pressure side of an injection system.
• the inlet bore comprises an inlet throttle, which limits the flow of high-pressure fuel into the control chamber.
• the control chamber is further connected via a drain hole with a low pressure side of the injector, wherein the drain hole is closed by a control valve.
• control valve For injecting high-pressure fuel into the combustion chamber of the internal combustion engine, the control valve can be opened, wherein the high-pressure fuel flows from the control chamber via the drain hole and a drain hole provided in the drain hole and as a result, the valve spool is released to open an injection nozzle ,
• the high-pressure fuel is introduced eccentrically via the inlet bore into the control chamber, so that the inflowing fuel generates a swirling flow within the control chamber, which has a rotational and a translational component.
• the rotating within the control chamber flow has an axis of rotation which is coaxial with the axis of the drain hole.
• the rotating fuel flow which is generated by the off-center supply of high-pressure fuel into the control chamber, continues in the form of a swirl into the drain hole. Due to the swirl and the resulting flow, a vortex filament is formed which extends along the axis of rotation of the rotating flow and in the vortex core of which a dead water area forms.
• the Totwasser is no longer available to transport the fuel, so that the fuel can flow only on the walls of the control chamber and the drain hole along.
• the vapor bubbles which result in an open control valve due to the high flow rate of the fuel and the change in the fuel pressure in the region of the drain hole are forced into the center of the rotating flow, ie in the vortex core, where the implosion of the vapor bubbles occurs. In this way it is prevented that the vapor bubbles implode in the vicinity of the wall limiting the drain hole or in the region of the valve seat of the control valve, so that material removal and thus damage by cavitation is avoided.
• the use of the principle underlying the invention makes it possible to provide injectors with a long service life, which are suitable for multiple injection and highest load.
• the inlet throttle extends the inlet throttle
• Inlet bore in a direction which is eccentric to the cross section of the control chamber.
• the axis of the inlet throttle and preferably also the axis of the entire inlet bore thus do not intersect the cross-sectional center of the control chamber.
• the generation of the rotating flow or the twist of the high-pressure fuel in the control chamber is thus by a simple structural measure, namely an eccentric arrangement of the inlet throttle in
• At least a portion is provided with a baffle surface, which deflects the high-pressure fuel, which flows into the control chamber via the inlet bore.
• a baffle surface which deflects the high-pressure fuel, which flows into the control chamber via the inlet bore.
• the drain hole comprises a diffuser which reduces the flow rate of the fuel and increases the fuel pressure.
• the diffuser is arranged on the control valve side facing the outlet throttle in the drain hole and thus in the flow direction of the fuel after the outlet throttle.
• the rotating flow continues as a vortex to the drain hole, the vortex is fully formed in the area of the outlet throttle and rotates at high speed.
• the air venting area of the vortex widens conically, whereby the vapor bubbles present in the vortex core are purposefully brought to implosion.
• the inventive arrangement of the diffuser after the outlet throttle thus results in the advantage that the cavitation takes place in the region of the drain hole in which it does not cause erosion.
• the diffuser has an optimized opening angle in a range of less than 15 ° or is cylindrical.
• the drain hole has a control-chamber-side bore portion which is arranged coaxially to the outlet throttle and has a larger inner diameter than the outlet throttle.
• the cross-sectional transition from the bore section to the outlet throttle can in this case be stepped, conical or in a rounded shape.
• the control-chamber-side bore section which preferably has a cylindrical shape, stabilizes the vortex core, which results from the rotating in the control room flow. The vortex core continues as vortex filament into the outlet throttle, which adjoins the bore section.
• the transition from the bore section to the outlet throttle has a conical shape, whereby flow turbulences in the transition region between the bore section and the outlet throttle are avoided.
• the drain hole has at its end facing the control chamber an inlet rounding.
• the drain hole at its end facing the control chamber has an inlet edge, which forms the transition between the control chamber and the drain hole.
• a further conical transition area is provided between the outlet throttle and the valve seat of the control valve.
• the further conical transition region which is provided at the end of the drainage bore facing the control valve and thereby forms the transition from the drainage bore to the valve seat of the control valve, is in this case designed as a chamfer.
• the control valve has a spherical valve body, which serves as a shut-off for the drain hole.
• the spherical valve body is in this case rotatably received in a corresponding guide of the control valve and can thus be offset by the swirl pulse of the fuel flow in rotation.
• the rotation of the valve ball has the advantage that the wear of the valve ball is reduced and extends the service life of the control valve.
• valve control piston is rotatable about its longitudinal axis taken up in the injector.
• the valve control piston is in this case displaceable by the swirl flow in a rotation, which advantageously reduces the wear of the valve spool and increases its life.
• Figure 1 is a schematic longitudinal section through an injector according to the invention, in the housing, a valve piece is inserted with a valve control piston;
• Figure 2a is a schematic cross-sectional view through the control chamber of a valve piece with an according to the invention by an angle eccentrically rotated inlet bore, which comprises an inlet throttle;
• Figure 2b is a schematic cross-sectional view through the control chamber of a valve piece with a centrally arranged countersink and an eccentrically offset according to the invention inlet throttle;
• FIG 3 is a schematic representation of the fuel flow in a control chamber of a valve piece of Figure 2a; such as
• Figure 4 is a schematic representation of a longitudinal section through a valve piece in the region of the drain hole with the drain hole occluding Ventilku- gel of a control valve.
• Figure 1 shows a partial view of an axial section through an injector 1 with a valve piece 4, which is inserted into a housing 2 of the injector 1.
• the valve piece 4 is arranged in a multi-stepped axial recess 6 of the housing 2, in which a valve spool 8 centered and axially and rotationally movably received.
• a nozzle body, not shown in Figure 1 in which a coaxial with the valve spool 8 arranged nozzle needle is provided which an injection nozzle for injecting high-pressure fuel in the combustion chamber of an internal combustion engine in phases opens.
• an axial bore 10 is provided, which extends in the axial direction of the valve member 4 therethrough and is divided into sections with different sized inner diameters.
• the axial bore 10 of the valve member 4 In a lower portion of the axial bore 10 of the valve member 4 while the valve spool 8 is movably received with its upper end in the axial direction, which results in a comparatively garger control chamber 12 in the valve piece 4 above the valve spool 8.
• the axial bore 10 provided in the valve piece 4 extends as far as a valve seat 16 of a control valve (not further illustrated in FIG. 1).
• the section of the axial bore 10 between the control chamber 12 and the valve seat 16 is in this case designed as a drain hole 14 and is by a not further illustrated in Figure 1 control valve with respect to the arranged above the valve piece 4 cavity of the axial recess 6 of the injector 2, which serves as a pressure equalization chamber , lockable.
• an inlet bore 20 is provided in the wall 18 of the valve member 4, which connects the control chamber 12 via an annular space 22 with a high pressure port 24. Via the high-pressure connection 24, the control chamber 12 is thus supplied with high-pressure fuel via the annular space 22 and the inlet bore 20, an inlet throttle 26 being provided in the inlet bore 20 for restricting the volume flow.
• FIG. 2 a and FIG. 2 b show two cross-sectional views of a control chamber 12 of a valve piece 4, which comprises an inlet bore 20 with an inlet throttle 26.
• the inlet bore 20 in this case connects the control chamber 12 arranged inside the valve piece 4 hydraulically with the annular space 22 of the injector 1 shown in FIG. 1.
• the inlet bore 20 next to the inlet throttle 26 extends into the control chamber 12 passes, in addition still a countersink with a cylindrical portion 28 and a conical portion 30.
• the inlet throttles 26 shown in Figure 2a and 2b are arranged eccentrically.
• an eccentrically arranged inlet throttle 20 shown in Figure 2a
• the axis of the inlet bore 20 and the inlet throttle 26 is rotated by an angle x relative to a radial orientation of the inlet bore.
• the cylindrical portion 28 of the inlet bore 20 is in this case arranged coaxially to the inlet throttle 26.
• Another embodiment of an eccentrically arranged Inlet bore 20 is shown in Figure 2b.
• the conical portion 30 and the cylindrical portion 28 of the inlet bore 20 are arranged centrally, whereas the inlet throttle 26 is eccentrically offset from a radial alignment by an offset e.
• the high-pressure fuel from the annular space 22 shown in Figure 1 flows tangentially into the control chamber 12, whereby a swirl flow with a translational and rotational component is formed.
• the swirl flow indicated by the arrows 34 in FIG. 3 thereby rotates in the direction of the arrow 32 within the control chamber 12, wherein a swirl core and a vortex thread are formed in the region of the axis 36 of the valve piece 4, which is indicated schematically by the reference numeral 38 in FIG are.
• the vortex filament represents the center line of the vortex core 38 extending in the axial direction of the axial bore 10 of the valve piece 4, which propagates along the direction of flow.
• this extends in a plurality of cross-sectional portions to the conically shaped valve seat 16 of the control valve.
• an outlet throttle 42 follows, followed by a diffuser 44.
• a conical transition region 46 may be arranged, which has a smaller cone diameter than the adjoining valve seat 16.
• the various sections 40, 42, 44 different sized inner diameter, wherein the cylindrical bore portion 40 the largest inner diameter and the outlet throttle 42 comprises the smallest inner diameter.
• the transition from the control chamber 12 to the cylindrical bore portion 40, the transition from the cylindrical bore portion 40 to the outlet throttle 42 and the transition from the outlet throttle 42 to the diffuser 44 are stepped.
• FIG 4 An alternative embodiment of the drain hole 14 is shown in FIG 4, in which an axial longitudinal section through the valve member 4 in the region of the drain hole 14 is shown.
• the transition from the control chamber 12 to the cylindrical bore portion 40 and the transition from the cylindrical bore portion 40 to the outlet throttle 42 is not in a stepped shape.
• a conical portion 48 of the drain hole 14 is arranged, which tapers from the control chamber 12 in the direction of the cylindrical bore portion 40 tapers.
• a circumferential chamfer 50 which has a larger cone diameter in the transition from the control chamber 12 to the drain hole 14 by the arrangement of the circumferential chamfer 50 and the Cone-shaped portions 48 in front of the cylindrical bore portion 40, a flow demolition in the region of the cross-sectional change between the control chamber 12 and the cylindrical bore portion 40 is prevented, whereby the vortex core 38 of the rotating flow is stabilized.
• the drainage bore 14 has an outlet opening at its end facing the control chamber 12, the edge of which is rounded.
• the cylindrical bore section 40 has a conical shape in the transitional region 52 to the outlet throttle 42.
• the transition from the outlet throttle 42 to the diffuser 44 is step-shaped.
• the diffuser 44 can hereby have an optimized opening angle of preferably less than 15 °, as a result of which the speed level of the swirl flow is reduced and the pressure level is increased.
• the vapor bubbles formed in the vortex core 38 of the swirl flow are due the increase in the pressure level in the region of the diffuser 44 is deliberately brought to implosion, without any damage being caused by cavitation erosion at the wall bounding the drainage bore 14.
• the effect according to the invention that no damage to the conical valve seat 16 occurs.
• a conical transition region 46 connects, which merges into a conical valve seat 16.
• the conical transition region 46 has a smaller cone diameter than the conical valve seat 16.
• the conical transition region 46 from FIGS. 1 and 4 represents a flow transition section, which can serve as a damage-relevant region for cavitation in front of the valve seat 16.
• the drain hole 14 is closed by a spherical valve body 54 which is rotatably guided by a ball guide, not shown in Figures 1 and 4 and actuated by an actuator, also not shown.
• the swirl impulse of the swirl flow allows the spherical valve body 54 to be set in rotation.
• the inlet bore 20 and the drain hole 14 have a combination of differently shaped transitions.
• the transitions between the sections of different inner diameters preferably have a conical or conical shape, a stepped shape or a rounded shape.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Fuel-Injection Apparatus (AREA)
• Lift Valve (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

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Citations (5)

Family Cites Families (1)

• 2008
  • 2008-09-23 DE DE200810042293 patent/DE102008042293A1/de not_active Withdrawn
• 2009
  • 2009-07-27 WO PCT/EP2009/059649 patent/WO2010034544A1/de active Application Filing
  • 2009-07-27 CN CN200980137491.1A patent/CN102165176B/zh active Active
  • 2009-07-27 EP EP09781113.7A patent/EP2347115B1/de active Active

Patent Citations (5)

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