EP1991773A1 - Soupape d'injection de carburant pour moteurs A combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs A combustion interne

Info

Publication number
EP1991773A1
EP1991773A1 EP07701891A EP07701891A EP1991773A1 EP 1991773 A1 EP1991773 A1 EP 1991773A1 EP 07701891 A EP07701891 A EP 07701891A EP 07701891 A EP07701891 A EP 07701891A EP 1991773 A1 EP1991773 A1 EP 1991773A1
Authority
EP
European Patent Office
Prior art keywords
injection valve
valve member
valve
chamber
fuel
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
Application number
EP07701891A
Other languages
German (de)
English (en)
Other versions
EP1991773B1 (fr
Inventor
Marco Ganser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ganser Hydromag AG
Original Assignee
Ganser Hydromag AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ganser Hydromag AG filed Critical Ganser Hydromag AG
Publication of EP1991773A1 publication Critical patent/EP1991773A1/fr
Application granted granted Critical
Publication of EP1991773B1 publication Critical patent/EP1991773B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F02M47/025—Hydraulically actuated valves draining the chamber to release the 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
    • 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
    • F02M47/027—Electrically actuated valves draining the chamber to release the 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
    • F02M55/004—Joints; Sealings
    • F02M55/005—Joints; Sealings for high pressure conduits, e.g. connected to pump outlet or to injector inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0028—Valves characterised by the valve actuating means hydraulic
    • F02M63/0029—Valves characterised by the valve actuating means hydraulic using a pilot valve controlling a hydraulic chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F02M63/0042—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing combined with valve seats of the lift valve type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing

Definitions

  • the present invention relates to a fuel injection valve for the intermittent injection of fuel into the combustion chamber of an internal combustion engine according to the preamble of patent claim 1, which is preferably used in diesel engines.
  • Fuel injection valves of this type are known, for example, from WO 2005/019637 A1. Further fuel injection valves are disclosed, for example, in WO 02/053904 A1, EP 0 976 924 B1 and DE 37 00 687 A1.
  • an injection valve with a piezoelectric actuator which controls an outlet of a valve chamber.
  • the valve chamber is connected via an outlet throttle passage with a control chamber and this control chamber is connected via an inlet throttle passage with a high pressure chamber of the injection valve.
  • the end face of a control piston of the injection valve member is relieved, whereby the injection valve member can be opened and the injection of fuel can take place.
  • the piezoelectric actuator another connected to the high-pressure chamber passage, whereby the inflow of fuel into the control chamber in addition to the intake throttle passage can also take place through the Auslassdrossel mallass.
  • a solenoid valve when actuated, connects a channel to a return line.
  • a control chamber Between the channel and a control chamber is designed as a plate with a throttle bore check valve.
  • the control chamber can empty only via the throttle bore of the check valve plate in the channel, resulting in a controllability of the opening movement of the injection valve member.
  • the fuel flow must flow to close the injection valve member alone by a throttle, which connects the channel via an annulus with a pressure accumulator of Einspritzsyster ⁇ s.
  • This throttle is tuned by small cross-section and with another throttle, which is located at the output of the channel.
  • the opening and closing movement of the injection valve member is thus controlled by three throttle bores, which must be precisely matched.
  • a fuel injection valve is known, in which the opening movement of the injection valve member, analogous to the disclosed in DE 37 00 687 Al injection valve, can be determined by designing a throttle bore.
  • the piezo actuator of a pilot valve must expand, which results in a high-pressure inlet connected to the high pressure passage is released by a control body.
  • the released, relatively large cross section causes a large fuel flow into the control chamber and thus a particularly rapid and advantageous closing of the injection valve member.
  • a transmission pin is pressed by a pilot valve pin of the actuator on the front side of the control body.
  • the piezo actuator must expand during the closing process of the injection valve member. In this state, a piezo actuator is energized. Since the duration of injection is only 5% or less of the duration between two injections, the piezoactuator is almost constantly under electrical voltage. Furthermore, in this known solution, the position of the throttle bore, which determines the opening movement of the injection valve member, unfavorable, since it is located far away from the control room.
  • Object of the present invention is to provide a fuel injection valve of particularly simple construction, in which both a controllability of the opening movement of the injection valve member and a rapid closing of the injection valve member can be achieved with a minimum construction cost. Furthermore, the fuel injection valve of the present invention, the realization of multiple injections can be easily achieved with a very short time interval.
  • an intermediate valve separates these two spaces continuously from one another.
  • the throttle passage is disposed immediately adjacent to the control room.
  • acting as a 2/3 way valve flat seat valve member is used, which can perform a certain, small stroke in a second intermediate plate in the valve chamber.
  • the flat seat valve member has two flat seats. In the discharged state of a piezoactuator used with advantage for actuating the
  • Flat seated valve member closes the flat seated valve member with a first valve seat, a connection between the valve chamber and the low-pressure fuel return from and at the same time releases a located in a first intermediate plate, connected to the high-pressure inlet high pressure passage of relatively large, unthrottled cross section.
  • the passage cross section between the flat seat valve member and the high pressure inlet, ie the valve seat, is dependent on the distance, thus the stroke of the flat seat valve member and usually represents a narrower passage than that of the high pressure passage.
  • Fig. 1 a longitudinal section of a
  • Fig. 2 a longitudinal section and in an enlarged view a partial section of the inventive
  • Fuel injection valve of Figure 1 with its control device for controlling the ⁇ réellesund rapid closing movement of the injection valve member.
  • FIG. 3 shows a diagram with the courses of the movements of the Aktuatorventilgliedes and the injection valve member of
  • FIG. 4 shows a longitudinal section and an enlarged view of a partial section of a first alternative design variant of
  • FIG. 5 shows a longitudinal section and in an enlarged view of a partial section of a second alternative design variant of
  • FIG. 6 is a longitudinal section and an enlarged view of a partial section of a third alternative design variant of
  • Control device of the fuel injection valve of the present invention is a longitudinal section and in an enlarged view of a partial section of a fourth alternative design variant of
  • FIG. 13 shows a perspective bottom view of the intermediate body.
  • Figure 1 shows a fuel injection valve 1, which is intended for the intermittent injection of fuel into the combustion chamber of an internal combustion engine. It has an elongate, circular cylindrical and stepped housing 6, the housing axis is denoted by 8.
  • the housing 6 consists of a housing body 10, a first intermediate plate 12, a second intermediate plate 14 and a nozzle body 16.
  • the first intermediate plate 12 and the second intermediate plate 14 form an intermediate part 17.
  • the intermediate plates 12 and 14 and the nozzle body 16 are provided with a Union nut formed clamping nut 18 in a tight manner against each other and clamped together against a lower surface 10 a of the housing body 10.
  • the first intermediate plate 12 rests against the nozzle body 16 and the second intermediate plate 14 on the housing body 10.
  • Fuel injector 1 is connected in a known manner to a fuel feed which supplies fuel to fuel injector 1 at very high pressure, for example up to 1800 bar or higher.
  • the high-pressure fuel inlet 20 opens laterally into the housing body 10, but could also be made more or less parallel to the housing axis 8 from above in the housing body 10.
  • In the high-pressure fuel inlet 20 opens a longitudinal bore 22, which is also made in the housing body 10 and the other end opens into the lower surface 10 a of the housing body 10.
  • the longitudinal bore 22 diametrically opposite and on a Aktuatorachse 8 ', the desachsiert with respect to the Housing axis 8 is, there is an actuator 24, which is preferably designed as a piezoelectric actuator 26 and could alternatively be designed as Elektromagnetaktuator.
  • a needle-shaped injection valve member 28 In a high-pressure chamber 42 of the nozzle body 16 are a needle-shaped injection valve member 28, a support sleeve 30, a washer 32, a compression spring 34 and a guide sleeve 36. About the washer and support sleeve 30, the compression spring 34 is supported on the injection valve member 28.
  • a bore 38 through the second intermediate plate 14 and a bore 40 through the first intermediate plate 12 connect the longitudinal bore 22 with the high-pressure chamber 42.
  • This high-pressure chamber 42 extends from the front side 16b of the intermediate plates 12, 14 facing
  • Nozzle body injection openings 44 'on The
  • Injection valve member 28 has a radial guide 46 with the nozzle body 16, which is interrupted by abutment surfaces 48 of the injection valve member 28 for hydraulically virtually resistant supply of high-pressure fuel to the injection valve seat 44.
  • first and the second intermediate plates 12 and 14 is a hydraulic control device 52 for
  • Fuel injection valve 1 is shown and described in detail in connection with FIG. One
  • Low pressure fuel return 50 relieves fuel to Control of the movements of the injection valve member and leads this fuel away from the fuel injection valve.
  • Fuel injector 1 Next, only the differences to the fuel injector 1 shown in the figure 1 or previously described embodiments are set forth below.
  • Figure 2 shows a longitudinal section and in an enlarged view of a portion of the inventive fuel injection valve 1 of Figure 1 with its control device 52 for controlling the opening and rapid closing movement of the injection valve member as presented in the pause time between two injection events.
  • a control piston 28 'of the injection valve member 28 is radially guided in a close sliding fit in the guide sleeve 36 and axially displaceably mounted. It limits together with the guide sleeve 36, the end face 36b of the spring
  • the recess 62 is connected by means of radial passages 56 '' in the head 60 with the control chamber 54 hydraulically permanently connected and thus part of the control chamber 54.
  • the head 60 is supported by a on a lower surface 14a of the second intermediate plate 14, small compression spring 66 pressed against a shoulder 64 of the guide sleeve 36.
  • a precise throttle passage 68 of the intermediate valve member 56 permanently connects the control chamber 54 with a valve chamber 70 in the second intermediate plate 14; a recess extending through the second intermediate plate 14 and delimited by the first intermediate plate 12 and the housing body 10 forms the valve space 70.
  • the valve space 70 is hydraulically connected via a passage 70 'to the back of the intermediate valve member 56; The small space in the through opening of the first intermediate plate 12 on the back of the intermediate valve member 56 thus forms a hydraulic part of the valve chamber 70.
  • the throttle passage 68 is shown in FIG. 2 immediately adjacent to the control chamber 54, could alternatively sunk along the in the axial direction be made by the intermediate valve member 56, hydraulic connection bore or at the other end of this communication bore in the shaft 58, which has no effect on the function of the fuel injection valve 1.
  • valve chamber 70 there is actuated by the piezo actuator 26 Aktuatorventilglied 72, which bears in its closed position, with its conical sealing surface, sealingly formed on a housing body 10, annular valve seat DS.
  • the valve seat DS is formed by the mouth of a housing body 10 in the housing Outlet passage 73 formed; this exhaust passage 73 leads to the low pressure fuel return 50.
  • An actuator valve member spring 74 exerts a constant but small spring force in the direction of the valve seat DS toward the actuator valve member 72, as compared to the fuel pressure force.
  • a bore 76 of relatively large cross section in the first intermediate plate 12 connects the control chamber 54, via a lateral passage in the second intermediate plate 14, with the bore 38.
  • the intermediate valve 56 ' is closed, this connection is interrupted, in its open position, the intermediate valve 56
  • the lateral passage may alternatively be made in the first intermediate plate 12.
  • the dimensions of the above-mentioned outlet passage, the bore orifice of the throttle passage are, for example, 0.20 mm for the throttle passage 68, 0.80 mm for the bore 76 and 1.3 mm for the valve seat DS of the Aktuatorventilgliedes 72 at a full opening stroke of the Aktuatorventilgliedes 72 of about 0.025 mm.
  • the latter corresponds to an outlet throttle passage 73 corresponding to a bore of approximately 0.36 mm diameter, all of which are indicative only.
  • the above data show that the sole essential control cross section, which is decisive for the opening movement of the injection valve member 28 when the actuator valve member 72 is open, is represented by the throttle passage 68.
  • the operation of the fuel injection valve 1 is as follows: the piezoelectric actuator 26 is energized, this expands and opens by means of movement of the Actuator valve member 72 down the valve seat DS and thus the outlet passage 73.
  • This position of the Aktuatorventilgliedes 72 is shown in Fig. 2 with a dashed line.
  • the fuel pressure in the valve chamber 70 drops rapidly. Thereby, the mushroom-shaped intermediate valve member 56 is moved away from its abutment on the shoulder 64 in the upward direction. Since the intermediate valve 56 'is still open, fuel from the bore 76 flows into the control chamber 54 until the intermediate valve 56 is closed, which happens when the flat top of the head 60 abuts the lower surface 12a. At this time, the pressure in the control chamber 54 has dropped little.
  • the intermediate valve member 56 can be moved by re-energizing the Piezoaktuators 26 during the closing movement of the injection valve member 28 again in the closing direction of the intermediate valve 56 'because the control chamber 54 and the distribution chamber 70, due to the sliding mount 58, are hydraulically practically separated.
  • the subsequent injection may be immediately adjacent to the end of the previous one, and the distance between the individual separate injections may be virtually reduced to zero.
  • this inventive control device 52 for controlling both small fuel injectors 1, such as for applications in passenger cars or truck engines, as well as much larger fuel injectors, which, for example, in locomotives Earthmoving machinery, power plants and ships.
  • Figure 3 shows the course of the movement of the injection valve member 28 in the event that the Aktuatorventilglied 72 during periods of not separate, but graduated injection operation, occupying a position between its maximum open and its closed position.
  • the timing of this actuator valve member lift, designated as "AH” is shown as AH (t) in the upper diagram of FIG. 3 such that downward movement of the actuator valve member (as shown in FIG. 2) opens or continues exhaust passage 73
  • the scale of AH and EH are different because, as already mentioned, the full opening stroke of the actuator valve member 72 is of the order of 0.025 mm and the full opening stroke EH of the injection valve member, as the case may be the engine size of a specific application is between 0.20 mm to over 1.0 mm.
  • the piezoactuator 26 is energized and the actuator valve member 72 opens, so that the opening movement of the injection valve member 28 begins at t 2.
  • the injection valve member 28 opens quickly but only travels a short distance, as the energization of the piezo actuator 26 is withdrawn and thus the actuator valve member 72 reduces the opening stroke to such an extent that the remaining outlet passage cross-section also acts as a throttle.
  • the opening speed of the injection valve member is kept greatly reduced until the piezoelectric actuator is fully energized again and the full speed of the opening stroke is restored, which is the case at t4.
  • the injection valve member 28 then opens again quickly up to t5 and its opening is controlled by the throttle passage 68. It is thus possible to realize a stepped injection course.
  • Figure 4 shows in longitudinal section and in an enlarged view a partial section of a first alternative design variant of the control device 52 'of the fuel injection valve 1.
  • the mushroom-shaped intermediate valve member 56 is completely recessed in the first intermediate plate 12 and forms together with the first intermediate plate 12, an intermediate valve 56' with conical Seat.
  • the remote from the end face 3 ⁇ b of the guide sleeve 36 shoulder 64 of Fig. 2 is omitted.
  • the guide sleeve 78 of FIG. 4 has a flat end surface 78b which, together with the lower surface 12a of the first intermediate plate 12 seals the control chamber 54 radially against the high-pressure chamber 42 and forms the abutment for the head 60 of the intermediate valve member 56.
  • the bore 76 opens directly into the bore 40.
  • the intermediate valve member 56 and the first intermediate plate 12 form a structural unit with a coordinated stroke of the intermediate valve member 56.
  • the intermediate part 17 forming two intermediate plates 12 and 14 could also consist of a single workpiece, which could also be realized in Figs. 1 and 2.
  • the embodiment according to FIG. 4 has a piston element 80.
  • This arrangement could also be used in the variant of FIG. 2.
  • the variant of FIG. 4 could also be realized without this piston element 80.
  • the piston element 80 is guided with a relatively narrow sliding fit 80 'in a blind hole-like recess in the first intermediate plate 12.
  • a small compression spring 82 constantly pushes the piston member 80 to the underside of the Aktuatorventilgliedes 72 at.
  • a space 84 in which the compression spring 82 is located and which is delimited by the underside of the piston element 80 is continuously hydraulically connected by means of a passage 86 with the recess 62 and via the passages 56 '' in the head 60 of the intermediate valve member 56 with the control chamber 54 ,
  • the operation of the arrangement of the intermediate valve member 56 with a conical valve seat is analogous to that of Figure 2.
  • the function of the piston member 80 is as follows: If the Aktuatorventilglied 72 is pressed by the piezo actuator 26 down, makes the piston member 80 with this movement. As a result, the piston member 80 increases the volume of the valve chamber 70 and at the same time reduces by its pumping action the volume of the space 84. Both cause a faster closure of the intermediate valve 56 ', since the intermediate valve member 56 is caused to move upwards more rapidly. Conversely, when the actuator valve member 72 moves upwardly, the piston member 80 causes an increase in the volume of the space 84 and at the same time a pumping action in the valve chamber 70. This causes a faster response of the intermediate valve member 56 when opening the intermediate valve 56 '. The piston member 80 thus supports a particularly rapid response of the intermediate valve member 56th
  • FIG. 5 shows in longitudinal section and in an enlarged view a partial section of a second alternative design variant of the control device 52 '' of the fuel injection valve of Figure 1.
  • the second intermediate plate 106 has no valve space, but only one outlet passage 110, which via a Passage 108 in the first intermediate plate 104, which the intermediate part 17 forming intermediate plates 104 and 106, in turn, could be realized as a single workpiece, is hydraulically connected to the back of the shaft 58 of the intermediate valve member 56.
  • the passage 108 could also be made in the second intermediate plate 106.
  • the valve chamber 70 of Fig. 5 is of particularly small volume content.
  • the cross section of the outlet passage 110 may be substantially larger than the cross section of the throttle passage 68.
  • the actuator shaft 112 in the position shown in FIG.
  • the actuator for the actuator shaft 112 may be either a piezo actuator or an electromagnetic actuator, which attracts the actuator shaft 112 in a known manner when energized.
  • Figure 6 shows in longitudinal section and in an enlarged view a partial section of a third alternative design variant of the control device 52 '''of the fuel injection valve 1.
  • the two intermediate plates 104 and 106 of the embodiment of Figure 5 are replaced by a single intermediate plate 105; it forms the intermediate part 17.
  • An outlet element 109 is located, coaxial with the desachs faced axis 8 ', in a recess of the intermediate plate 105 and is pressed by a plate spring 107 and the fuel pressure in the valve chamber 70 to the lower surface 10 a of the housing body 10, or alternatively a support member unspecified, sealing in abutment.
  • the outlet passage 110 is located in the outlet element 109.
  • the advantages of this variant are the use of a single intermediate plate 105 instead of two intermediate plates 104 and 106 and the fact that the outlet element 109, which is of small dimensions, is of a very wear-resistant and also expensive Material can be produced inexpensively.
  • a dashed line shows an alternative in FIG. 6, in which a throttle passage 77 connects the bore 40 with the small valve chamber 70. This causes a very rapid opening of the intermediate valve member 56 as soon as the outlet side of the outlet passage 110 is closed.
  • FIG. 7 shows, in a longitudinal section and in an enlarged view, a partial section of a fourth alternative construction variant of the control device
  • control device 88 is located in a high-pressure space 90, which is the same
  • Function has like the high pressure chamber 42 and in a
  • High-pressure chamber 90 surrounding body 92 is made.
  • Body 92 could be a nozzle body 16 or a housing body
  • High-pressure chamber 90 protrudes the control piston 28 'of the
  • Injection valve member 28 and the compression spring 34 presses the flat surface 78b of the guide sleeve 78 in tight engagement with a lower end surface 94a of an intermediate element 94, in which the mushroom-shaped intermediate valve member 56 is guided in a close sliding fit 94 '.
  • a bore 96 in the intermediate member 94 connects the recess 62 in which the intermediate valve member 56 is located, and a groove 96 'around the shaft 58 of the intermediate valve member 56 with a passage 98 and thus the high-pressure chamber 90.
  • the intermediate member 94 is in place of the first intermediate plate 12 of Figures 1, 2, 4 and 5 and is guided by a radially inner wall 100 of the body 92 with play on the circumference and axially aligned with the longitudinal axis 102.
  • the outlet passage 110 is located in a disc-shaped outlet member 114, which is positioned radially analogously to the intermediate member 94 of the wall 100 with clearance.
  • the upper side 114b of the outlet element 114 and the lower side 116a of a closing element 116 similar to the housing body 10, close off the high-pressure chamber 90 in a known manner in a pressure-tight manner.
  • the intermediate element 94 and the outlet element 114 form the intermediate part 17. Also in the embodiment according to FIG. 7, like that according to FIG.
  • the volume content of the valve space 70 is very small.
  • the end face of the shaft 58 of the intermediate valve member 56 can be depressurized and loaded by means of actuation of the actuator shaft 112 in order to realize intermittent diesel injections.
  • the solution of Fig. 7 is advantageous if the control device 88 is installed to save space in a bore on the axis 102 of the fuel injection valve and is dispensed with the intermediate plates 12, 14, 104, 105 and 106 of the preceding figures.
  • the intermediate member 94 and the outlet member 114 could be made together in one piece.
  • the throttle passage 77 connects the high-pressure chamber 90 with the valve chamber 70, which is shown in dashed lines and has the same effect as in FIG. 6.
  • Figure 7 has a mechanical stroke stop 79 for the face of the control piston 28 'of the injection valve member 28 in the form of a wall integral with the guide sleeve 78 projecting into the control chamber 54 and provided with a central passage 79b which connects the control chamber 54 with the recess 62 hydraulically.
  • a mechanical stroke stop 79 for the face of the control piston 28 'of the injection valve member 28 in the form of a wall integral with the guide sleeve 78 projecting into the control chamber 54 and provided with a central passage 79b which connects the control chamber 54 with the recess 62 hydraulically.
  • This or an embodiment corresponding in its function could also be used in the embodiments according to the other figures.
  • the embodiment shown in Fig. 7 can also be performed without mechanical stroke stop 79.
  • Actuator axis 8 ' is located.
  • FIG. 8 shows in longitudinal section and in an enlarged view a partial section of a fifth alternative construction variant of the control device 88 of the fuel injection valve, which is similar to that of FIG.
  • the mushroom-shaped intermediate valve member 56 has a flat seat as shown in FIG. However, there is no groove 76 'in the intermediate element 94 available.
  • Two opposing holes 96 in the intermediate member 94 (it could also be a bore 96 or more than two holes 96) form with its open inlet into the recess 62 together with the intermediate valve member 56, the intermediate valve 56 '.
  • FIG. 2 or the corresponding position of the preceding figures in the valve chamber 70 is very large, which does not occur with the variant of FIG. 8, because in addition to the closing of the holes 96, by means of the intermediate valve 56 ', also the sliding fit 94'' from the high pressure room 90 is separated. However, the sliding fit 94 '' must cause at least one such hydraulic separation point in this variant, which produces a sufficient pressure difference, so that after actuation of the actuator assembly 24, the intermediate valve member 56 very quickly completes the holes 96.
  • the outlet of the bores 96 may be widened in the recess 62 on the circumference about the axis 102 in order to obtain a larger flow area with a small stroke of the intermediate valve member 56.
  • FIG. 9 shows in longitudinal section and in an enlarged view a partial section of a sixth alternative construction variant of a control device 140 of the fuel injection valve of the present invention.
  • the second intermediate plate 14 is a acting as a 2/3 way valve, pill-like flat seat valve member
  • the flat seated valve member 120 which of a valve pin 122, for example can be actuated by a piezo actuator, can be moved.
  • the flat seated valve member 120 may perform a specific small stroke in the second intermediate plate 14, between the housing body 10 and the first intermediate plate 12.
  • the flat seat valve member 120 has two flat seats, because it is thus particularly easy to obtain the particular small stroke by the difference in the thickness of the second intermediate plate 14 and the thickness of the flat seat valve member 120.
  • the flat seat valve member with a first valve seat 124 closes the connection between the valve chamber 70 and the low-pressure fuel return 50 (see FIG.
  • the high-pressure passage 126 itself defining a sufficiently large circumferential seat cross-section with the valve seat 128, but an extension of the high-pressure passage 126 could also be formed in the region of the valve seat 128, of whatever geometric shape, to create a lateral surface on the valve seat 128, which is substantially larger than the passage of the throttle passage 68.
  • the lateral passage 70 'and a central passage bore 138 in the first intermediate plate 12 of relatively large cross-section connect the valve space 70 to the throttle passage 68 in the intermediate plate 132, which has lateral recesses 136 and pressed by a compression spring 134 to the lower surface 12 a of the first intermediate plate 12 becomes.
  • the passage bore 138 could also be arranged obliquely, so that the passage 70 'can be omitted.
  • the function of the control device 140 is as follows: for injection, the actuator assembly pushes the flat seat valve member 120 from its abutment position on the first valve seat 124 to the upper surface 12b of the first intermediate plate 12 by means of the valve pin 122, thus opening the first valve seat 124 to the low pressure outlet 50 and closing it As a result, the pressure in the valve chamber 70 drops and consequently also in the control chamber 54.
  • the injection valve member 28 can open and the opening movement is controlled by the throttle passage 68. If the first valve seat 124 is closed by the movement of the flat seat valve member 120 to terminate the injection, the second valve seat 128 opens at the same time.
  • the fuel flow entering the valve space 70 and the passage bore 138 through relatively large cross sections opens the intermediate plate by moving it from its installation is pushed away on the lower surface 12 a.
  • the recesses 132 of Brennstoffström passes into the control chamber 54 and the injection process is completed quickly.
  • multiple actuation of the actuator assembly Thus, multiple injections can be realized with a very short time interval.
  • the intermediate plates 12 and 14 can be integrally realized from a workpiece.
  • FIG. 10 shows, in longitudinal section and in an enlarged view, a partial section of a seventh alternative design variant of the control device 142 of the fuel injection valve of the present invention, which is similar to the embodiment of FIG.
  • the exact throttle passage 68 is located in the flat seat valve member 144 and communicates via the passage bore 146 of relatively large cross-section with the control chamber 54.
  • the passage bore 146 in the first intermediate plate 12 is arranged obliquely.
  • the throttle passage 68 must be aligned with the passage bore 146. This is ensured when the flat seat valve member 144 is not circular, but for example, has two chamfered surfaces laterally or oval or (right) is angularly aligned with an associated guide shape of the valve chamber 70 of the second intermediate plate 14 on the circumference.
  • a groove 146b in the first intermediate plate 12 (shown in phantom) or in the flat seat valve member 144 could ensure the hydraulic connection with a circular shape of the flat seat valve member 144. Since the passage bore 146 and also any distance in the groove 146b are short, the effect of the changed position of the throttle passage 68 is functionally the same as if the throttle passage 68 would be geometrically connected directly to the control chamber.
  • intermediate plates 12 and 14 could be combined to form a workpiece.
  • control device 142 The function of the control device 142 is analogous to that of FIG. 9. The construction is simpler since in FIG. 10 the intermediate plate 132 and the compression spring 134 are not needed.
  • the intermediate element 94 and the outlet element 114 of the embodiment shown in FIG. 8 are combined to form a single workpiece, an intermediate body 150.
  • the intermediate part 17 forming the disc-like intermediate body 150 is held by means of the clamping nut 18 sealingly on the one hand on the nozzle body 16 and on the other hand on the housing body 10 in abutment.
  • FIGS. 12 and 13 show the intermediate body 150 enlarged.
  • a downwardly open, blind hole-like recess in the intermediate body 150 forms with its circular cylindrical
  • blind hole-like recess extend through the intermediate body 150 through three holes 96, which are on the overhead side by a substantially V-shaped connecting groove 154 with the longitudinal bore 22 interference connected. On the lower side they open into the control chamber 54 and are closed by means of the head of the intermediate valve member 56.
  • the guide sleeve 78 is held with its end face 78b on the intermediate body 150 in close contact with the guide sleeve 78 between the U-shaped distribution groove 156 and the mouth of the holes 96 abuts the intermediate body 150.
  • the guide sleeve 78 compared with the region of the close sliding fit with the control piston 28 'of the injection valve member 28, extended formed to accommodate the head of the intermediate valve member 56 with sufficient radial play.
  • the intermediate body 150 has two blind-hole-like positioning holes 158 into which positioning pins on the housing body 10 engage.
  • the annular region extending around the mouth of the outlet passage 110 and cooperating with the flat end face of the actuator shaft 112, forming a valve seat, can be hardened.
  • a variant is shown in Fig. 11 in an analogous manner as described above, where the intermediate body 150 consists of two parts which are separated from each other.
  • the actuator shaft 112 closes the outlet passage 110, the injection valve member 28 abuts the injection valve seat 44, and the intermediate valve 56 'is opened; his head abuts an inner shoulder of the guide sleeve 78.
  • the actuator shaft 112 is retracted, resulting in a pressure drop in the valve chamber 70, because the flow cross section of the outlet passage 110 is substantially greater than the sum of the flow cross sections of the throttle passage 68 and the inlet bore 152. This has the consequence that the intermediate valve 56th 'closes and the pressure in the control room 54 therefore falls very quickly.
  • the injection valve member 28 is lifted by the pressure drop in the control chamber 54 against the action of the compression spring 34 from the injection valve seat 44.
  • the outlet passage 110 is closed by means of the actuator shaft 112. It comes very quickly to an at least approximate pressure equalization between the control chamber 54 and the valve chamber 70.
  • FIG. 11 also works without an admission bore 152.
  • the intermediate valve 56 ' is being pulled in, it is slightly delayed.
  • control devices of the fuel injectors of the present invention may also be used singly or in combinations other than those shown herein.

Landscapes

  • 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)

Abstract

Le dispositif de commande (52) de la soupape d'injection de carburant de l'invention présente un organe intermédiaire de soupape (56) en forme de champignon guidé avec un ajustement coulissant (58') dans une première plaque intermédiaire (12). L'organe de soupape d'injection (28) qui présente un piston pilote (28') et qui sert à ouvrir et fermer des ouvertures d'injection en vue de réaliser des opérations intermittentes d'injection définit une première chambre pilote (54) avec une douille de guidage (36) et la surface inférieure (12a) de la plaque intermédiaire (12). Une deuxième plaque intermédiaire (14) est située entre la première plaque intermédiaire (12) et le corps (10) du boîtier et présente un espace de soupape (70) qui est relié à écoulement au côté frontal de la tige (58) de l'organe intermédiaire de soupape (56) en forme de champignon.
EP07701891.9A 2006-03-03 2007-02-22 Soupape d'injection de carburant pour moteurs a combustion interne Active EP1991773B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3402006 2006-03-03
PCT/CH2007/000091 WO2007098621A1 (fr) 2006-03-03 2007-02-22 Soupape d'injection de carburant pour moteurs A combustion interne

Publications (2)

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EP1991773A1 true EP1991773A1 (fr) 2008-11-19
EP1991773B1 EP1991773B1 (fr) 2013-05-15

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Country Link
US (1) US8544771B2 (fr)
EP (1) EP1991773B1 (fr)
JP (1) JP5110321B2 (fr)
CN (2) CN102828872B (fr)
BR (1) BRPI0708551B1 (fr)
RU (1) RU2438035C2 (fr)
WO (1) WO2007098621A1 (fr)
ZA (1) ZA200807310B (fr)

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Also Published As

Publication number Publication date
CN101395366B (zh) 2012-09-12
JP2009528480A (ja) 2009-08-06
RU2008139317A (ru) 2010-04-10
US20090065614A1 (en) 2009-03-12
CN101395366A (zh) 2009-03-25
CN102828872B (zh) 2015-09-02
RU2438035C2 (ru) 2011-12-27
CN102828872A (zh) 2012-12-19
US8544771B2 (en) 2013-10-01
EP1991773B1 (fr) 2013-05-15
ZA200807310B (en) 2009-11-25
BRPI0708551A2 (pt) 2011-05-31
BRPI0708551B1 (pt) 2019-07-02
WO2007098621A1 (fr) 2007-09-07
JP5110321B2 (ja) 2012-12-26

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