EP0114375B1 - Fuel injection device for compression ignition internal combustion engines - Google Patents

Fuel injection device for compression ignition internal combustion engines Download PDF

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Publication number
EP0114375B1
EP0114375B1 EP83112959A EP83112959A EP0114375B1 EP 0114375 B1 EP0114375 B1 EP 0114375B1 EP 83112959 A EP83112959 A EP 83112959A EP 83112959 A EP83112959 A EP 83112959A EP 0114375 B1 EP0114375 B1 EP 0114375B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
characterized
regulator
appliance according
piston slide
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.)
Expired
Application number
EP83112959A
Other languages
German (de)
French (fr)
Other versions
EP0114375A2 (en
EP0114375A3 (en
Inventor
Gerd Wallenfang
Reda Rizk
Hans-Gottfried Michels
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.)
Kloeckner Humboldt Deutz AG
Original Assignee
Kloeckner Humboldt Deutz 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
Priority to DE3302294 priority Critical
Priority to DE19833302294 priority patent/DE3302294A1/en
Application filed by Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Publication of EP0114375A2 publication Critical patent/EP0114375A2/en
Publication of EP0114375A3 publication Critical patent/EP0114375A3/en
Application granted granted Critical
Publication of EP0114375B1 publication Critical patent/EP0114375B1/en
Expired legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46Valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20Varying fuel delivery in quantity or timing
    • F02M59/36Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366Valves being actuated electrically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46Valves
    • F02M59/466Electrically operated valves, e.g. using electromagnetic or piezo-electric operating means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02BINTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00Engines characterised by air compression and subsequent fuel addition
    • F02B3/06Engines characterised by air compression and subsequent fuel addition with compression ignition
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24Fuel-injection apparatus with sensors

Description

  • The invention relates to a fuel injection device for an air-compressing, self-igniting internal combustion engine according to the preamble of claim 1.
  • Such a fuel injection device is shown in DE-A-2 903 482, which has an electromagnetic actuator for the piston valve. According to the description in this laid-open publication, the valve member is brought into its closed position when the winding is excited, while when the winding is de-energized, the valve member is moved into the open position by the spring. Due to the direct coupling of the actuating element of the electromagnetic actuating device to the piston slide, the overall arrangement for opening the valve element must be accelerated. Large spring forces are required for this on the one hand, but on the other hand counteract rapid closing of the valve element when the electromagnetic actuating device is excited. The extremely short injection times in a diesel internal combustion engine to achieve minimal consumption and optimal exhaust gas behavior cannot be achieved with the proposed device.
  • From DE-A-2 026 665 a fuel injection device is known, the electromagnetic control valve of which is controlled by the electrically operating measured value processing device as a function of characteristic operating parameters of the internal combustion engine. The control valve controls an outflow channel provided on the nozzle side, in particular in order to regulate the start of injection and the end of injection of the fuel injection device with regard to the load state of the internal combustion engine. The spool of the electromagnetic control valve has the same cross-section over its entire length because the pump pressure is applied to the end face via pressure compensation lines, in particular to keep the required magnetic valve actuating forces on the control spool low. The spool of the control valve performs uncontrollable movements in the closed position, thus showing an unstable behavior, which is due in particular to uneven pressurization of the end faces of the spool, e.g. B. due to different pressure waves or more or less strong voiding in the pressure compensation lines. Furthermore, a more or less strong formation of cavities in the high-pressure system during the nozzle-side cut-off and the pump-side delivery further influences the injection time control.
  • From DE-A-3 002 361 it is known to dimension the pressure application areas of the high pressure chamber of the piston valve differently and to provide a fixed throttle in the outflow channel. On the one hand, the throttled outflow prevents rapid pressure reduction at the end of injection in the sense of a favorable consumption and emission behavior of the internal combustion engine and, on the other hand, a fixed-value throttle cannot do justice to different operating points of the internal combustion engine due to the different discharge quantities.
  • The invention has for its object to develop the known fuel injection device such that extremely short injection times can be achieved.
  • This object is achieved according to the characterizing features of claim 1.
  • The arrangement of an adjusting device for the closing movement and another adjusting device for the opening movement makes it advantageously possible to adapt them to the individual movements. Due to the inventive design of the electromagnetic actuating device for the opening of the piston valve, the actuator of which only hits the piston valve after a preliminary stroke and actuates it in the direction of opening, the actuator element - before transmitting an opening movement to the piston valve - acquires considerable kinetic energy which impulses on the Piston slide is transmitted and this is suddenly transferred to the open position. As a result, extremely short opening times can be achieved, as a result of which the amounts of fuel to be injected can be metered more accurately and also smaller.
  • The design of the fuel injection device according to the invention is not suggested by the further publications FR-A-1 566 847 and FR-A-2 465 085. For example, FR-A-1 566 847 relates only to configurations with two windings, which are intended to increase the electromagnetic force for performing a closing movement. This publication does not contain an actuating device which opens a piston slide in the opening direction after passing through a preliminary stroke path. FR-A-2 465 085 shows no two known electromagnetic actuating devices which work together in the manner according to the invention.
  • The housing space of the control valve has a high-pressure side and a low-pressure side housing space chamber which are assigned to the end faces of the piston valve, the high-pressure side and the low-pressure side housing space chamber being connected to one another by at least one line. The end face of the spool is larger in the high-pressure chamber chamber than that in the low-pressure chamber Housing chamber. With this configuration, it is possible to dispense with any additional pressure compensation lines, while maintaining pressure equalization and thus the advantage of low actuating forces on the end faces of the spool, so that any pressure discrepancies or pressure differences in the pressure compensation lines can also cause no interference on the control valve. Again, given the very high injection pressures sought and a correspondingly very short injection duration, this can be of decisive importance for the implementation of the control times determined by the electrically working measured value processing device for the start of injection and the end of injection of the fuel injection device. Furthermore, these refinements of the fuel injection device according to the invention advantageously support the resulting closing pressure force acting in the closed position of the piston valve. This is due in particular to the fact that in the closed position of the piston valve, the housing chamber chamber on the high-pressure side and the low-pressure chamber chamber on the low-pressure side are filled with fuel via the sealing gap between the high-pressure piston valve region and the housing chamber. During the opening movement of the spool, the fuel of the high-pressure side housing chamber is displaced into the low-pressure side housing chamber, so that fuel is compressed by the stroke movement due to the differently dimensioned piston spool areas, which flows out via the low-pressure sealing gap. In the high-pressure phase, i.e. the closed position of the piston valve, this fuel, which has flowed off on the low-pressure side, is refilled via the high-pressure channel and the high-pressure side sealing gap, with a pressure drop occurring in the direction of the low-pressure side housing chamber during the filling process, which causes the additional closing pressure force on the piston valve.
  • Further advantageous refinements of the invention, in particular for realizing a rapid valve body actuation which is advantageous for precise control of the injection process and optimizing the overall space requirement of the electromagnetic actuating device, are evident from the subclaims in conjunction with the description of the drawings.
  • For a further explanation of the invention, reference is made to the drawings, in which parts which basically have the same effect are provided with the same reference numbers. Show it:
    • 1 shows a cross section through an embodiment of a fuel injection device according to the invention.
    • 2 shows a schematic cross-sectional illustration of a control valve according to the invention;
    • 3 shows an exemplary embodiment of a fuel injection device according to the invention with an electromagnetic actuating device designed according to the invention in a cross-sectional illustration;
    • 4 shows a fuel injection device according to the invention with an alternative embodiment of an electromagnetic actuating device according to the invention in a cross-sectional illustration;
    • 5 shows a fuel injection device according to the invention, in which the control valve is provided in a holding element which can be adapted to the fuel injection pump.
  • In Fig. 1, a fuel injection device according to the invention is shown in cross section. The fuel injection device is provided in the usual way with a fuel injection pump 1, which consists of a pump housing 2, a pump element 3 designed as a pump piston, which can be moved in a known manner via a cam 4 and a spring-loaded tappet 5 in a pump chamber 6, an intake duct 7 and a high-pressure duct 8. The fuel is supplied to the pump work chamber 6 of the fuel injection pump 1 via a suction channel 7 from a fuel feed pump, not shown, and is conveyed to a fuel injection nozzle 10 via a high-pressure channel 8 during the stroke of the pump piston 3 through the high-pressure channel 8.
  • The high-pressure channel 8 is controlled by an electromagnetic control valve 11, which has a valve body designed as a piston slide 12 and loaded by a compression spring 13, which is operatively connected to an electromagnetic actuating device 14 in the opening direction. Via the electromagnetic control valve 11, the high-pressure channel 8 in the open position of the control valve 11 can be connected to an outflow channel 15 leading, for example, into a fuel tank, so that opening or closing of the electromagnetic control valve 11 in the high-pressure phase of the fuel injection pump 1 starts and ends the injection the fuel injector 10 is adjustable. The electromagnetic actuation device 14 is actuated for control valve actuation by an electrically working measured value processing device, not shown, which interacts with suitable sensors and, depending on the load condition of the air-compressing, self-igniting internal combustion engine equipped with the fuel injection device according to the invention, regulates the activation times and thus the start of injection and the end of injection. The spool 12 of the electromagnetic control valve 11 has a high-pressure side spool part 17 delimited by a valve body 16 and a low-pressure side spool part 18, the high-pressure side spool part 17 constantly having the diameter of the valve body 16 and the low-pressure side spool part 18 having a smaller diameter than the high-pressure side spool part 17 is trained. The piston slide 12 is axially movable in a housing space 19, the housing space 19 having a high-pressure-side housing space chamber 20 and a low-pressure-side housing space chamber 21, which are each assigned to the end faces of the piston slide 12, and wherein the housing space 19 outside a high-pressure chamber 22 and a low-pressure chamber 23 suitable sealing elements 24 is sealed pressure-tight. The high-pressure-side housing space chamber 20 and the low-pressure-side housing space chamber 21 are connected to one another by a bore 25 which is not visible in the illustration according to FIG. 1. The opening movement of the piston slide 12 is limited by a stop 27, as is the compression spring 13 arranged in the high-pressure-side housing chamber 20, the stop 27, the compression spring 13 and the electromagnetic actuating device 14 in order to generate a resulting pressure closing force in such a manner on the end faces of the Piston slide 12 are provided or the end faces of the piston slide 12 are designed such that the end face area of the piston slide 12 exposed to the high-pressure side chamber pressure is larger than the end face area of the piston slide 12 which is exposed to the low pressure side chamber pressure.
  • The pump piston 3 has in its lateral surface a longitudinal groove 42 which is in flow connection with the pump chamber 6 and can be brought into overlap with the suction channel 7 by rotating the pump piston 3. To rotate the pump piston 3, a mechanical control device (not shown in more detail) is provided, which works as a function of the speed using generally known means, for example centrifugal weights etc., and at a predeterminable maximum speed of the internal combustion engine releases the connection between the pump chamber 6 and the intake duct 7 for the purpose of controlling fuel . This measure serves as an additional safety device.
  • The mode of operation and the advantages of the control valve designed according to the invention are to be explained in more detail with reference to the schematic illustration of the control valve according to FIG. 2, wherein in this illustration the valve actuation elements, such as compression spring, electromagnetic actuator connection and the like, have been omitted for the sake of a better overview. Due to the high-pressure piston valve design with a smooth transition in the valve body 16, there is no pressure contact surface for the very high fuel pressure, so that possible unstable, uneven pressure distributions on the piston valve 12 cannot exert any influence in the closed position, which is decisive for the controllable injection process. During the high pressure phase of the fuel injection, fuel is conveyed to the fuel injection nozzle 10 via the high pressure channel 8 via the high pressure chamber 22 of the control valve 11. In this case, there is a pressure drop across the sealing gap 28a in the high-pressure-side housing space chamber 20 and thus via the bore 25 also to the low-pressure-side housing space chamber 21, which always ensures that the chamber system is filled with fuel. The opening movement of the piston valve 12 displaces fuel from the high-pressure side housing chamber 20 into the low-pressure side housing chamber 21, the fuel in the housing chamber chambers being compressed due to the difference in diameter of the end faces of the piston valve 12. This excess pressure is reduced in the open position of the spool 12 by fuel flowing out via the low-pressure side sealing gaps 28b. This amount of fuel that has flowed out is replenished in the closed position of the spool 12 due to the pressure drop across the high-pressure sealing gaps 28a, the filling process during the high pressure phase exerting a further pressure-closing force on the spool 12, which supports the tightness of the control valve, so that the control valve 11 advantageously is optimized in the sense of absolute tightness in the closed position.
  • FIG. 3 shows the fuel injection device according to the invention corresponding to FIG. 1 with an electromagnetic actuation device 14 designed according to the invention, although the known parts of the fuel injection pump have not been shown. The electromagnetic actuating device 14 according to the invention shown in the exemplary embodiment according to FIG. 3 is designed in such a way that the piston slide 12 can be actuated in the opening direction after a forward stroke of the actuating device, in particular by to use the impact generated in the sense of very fast opening times and thus precise control of the spool 12 For this purpose, the electrical actuating device 14 has a second electromagnetic actuating device (coil) 29 with an iron core 30 and an armature 31, a spring element 32 being fastened to the armature 31, which spring element can be pretensioned by the excitation of the actuating device 29 by the movement of the armature 31 , and wherein the preload of the spring element 32 is limited by a spacer 33. Furthermore, the electromagnetic actuation device has a first electromagnetic actuation (coil) 34 with a two-part armature and an iron core 36. The two-piece armature consists of an inner armature part 35a and an outer armature part 35b, the inner armature part 35a being axially movable relative to the outer armature part 35b and being able to be coupled thereto in a fixed manner via a shoulder / collar connection 37. In the exemplary embodiment according to FIG. 3, the second actuating device 29 with the associated armature 31 and the iron core 30 and the first actuating device 34 with associated armature parts 35a and 35b and the second iron core 36 are assigned to the low-pressure-side housing space chamber 21 and provided with corresponding sealing elements 24, whereby the inner armature part 35a of the first actuating device 34 acts directly on the piston slide 12 and the armature 31 of the second actuating device 29 is in direct operative connection with the inner armature part 35a of the first actuating device 34. Between the second adjusting device 29 and the first adjusting device 34, a stop element 38 is further provided, which limits the axial lifting movement of the outer armature part 35b of the first adjusting device 34 to one side, the stop element 38 and the spacer element 33 being designed such that between the inner armature part 35a of the first actuating device 34 in the closed position of the spool 12 and the armature 31 of the second actuating device 29 with a maximum preloaded spring element 32, a preliminary stroke distance is present. The axial stroke movement of the outer armature part 35b is limited on the other hand by a non-magnetic spacer 41 towards the iron core 36.
  • During the operation of the fuel injection device according to the invention, the actuating devices 29 and 34 are activated as a function of the control times determined by the electrically working measured value processing device. Here, the second actuating device 29 is energized and the first actuating device 34 is de-energized during the closed position of the spool 12, so that the spring element 32 is pretensioned to a maximum and the outer armature part 35b rests on the stop element 38 and there is a preliminary stroke distance between the inner armature part 35a and armature 31 . When the opening signal is generated by the electrically working measured value processing device d. H. End of injection, the second actuating device 29 is switched off, so that initially only the armature 31, and thus advantageously a very small mass, is accelerated by the spring element 32 and after the preliminary stroke via the inner armature 35a, the piston slide 12 opens suddenly as far as the stop 27, the outer armature 35b of the first actuating device 34 initially remains in the rest position due to the relative possibility of axial movement of the inner armature 35a. After the opening movement of the piston slide 12, the first actuating device 34 is excited so that the outer armature part 35b is brought into contact with the spacer 41. Due to the re-excitation of the second actuating device 29, the spring element 32 is pretensioned again and the armature 31 is brought back into the pretension position. The adjusting device 34 now takes over the holding function of the piston slide 12 against the force of the compression spring 13, the piston slide stroke now no longer being limited by the stop 27, but rather by the inner armature part 35a resting on the outer armature part 35b via the shoulder / collar connection 37.
  • The closing movement of the piston slide 12 is initiated by switching off the first adjusting device 34, so that the compression spring 13 brings the piston slide 12 into the closed position, although in this case advantageously only the armature parts 35a and 35b need to be carried along.
  • This inventive design of the electromagnetic actuating device 14 makes it possible in an advantageous manner to have the magnetic actuating forces to be applied and thus the construction volume claimed low due to the predominant holding function of the first actuating device 34 and the second actuating device 29.
  • A sensor device 40 is provided in the range of movement of the low-pressure side end face of the piston slide 17, which - not shown in detail - has a permanent magnet, pole shoes and an induction coil and, depending on the piston slide movement or an air gap between the piston slide face and the inner armature 35a., Generates an impulsive signal which can be evaluated in the measured value processing device as a closing time or opening time signal of the control valve and can be taken into account accordingly when controlling the actuating devices 29 and 34 to avoid magnetic transmission errors, although the local arrangement shown here Sensor device 40 is not mandatory, but also preferably the one or a second sensor device 40 can be provided between the armature 31 and the outer and inner armature parts 35a and 35b.
  • The embodiment according to FIG. 4 is designed similarly to the embodiment according to FIG. 3, but with the second adjusting device 29, the iron core 30 and the anchor 31 of the low-pressure housing space chamber 21 and the first adjusting device 34 and the inner anchor part 35a, the outer anchor part 35b and the iron core 36 are assigned to the housing chamber 20 on the high-pressure side, again suitable sealing elements 24 being provided for the pressure-tight sealing of the housing chambers 20, 21. In this exemplary embodiment, the armature 31 of the second actuating device 29 is in direct operative connection with the piston slide 12 and the inner armature part 35a is fastened directly on the piston slide. To actuate the spool 12 in the opening direction after a forward stroke of the electromagnetic actuating device 14, the spacing element 33 is designed in this embodiment such that in the closed position of the spool 12, the armature 31 can be moved by an excitation of the second actuating device 29 into an axial distance from the spool 12 is. The iron core 36 has a shoulder 36a designed as a spacer element, which interacts with the inner anchor parts 35a.
  • The excitation times or the excitation duration of the second actuating device 29 of the first actuating device 34 determined by the electrically operating measured value processing device takes place in an analogous manner to that in the exemplary embodiment according to FIG. H. that the actuating device 29 can be switched off for valve opening, as a result of which the injection process is ended during the high-pressure phase of the fuel injection pump 1 and thus the end of injection is determined, and the valve closing process is initiated by switching off the first actuating device 34, the piston slide 12 moving under the force of the compression spring 13 moved into the closed position and thus the start of injection of the fuel injection device is determined. The advantages indicated in connection with FIG. 3 apply analogously to this exemplary embodiment.
  • In the embodiment of the fuel injection device according to the invention shown in FIG. 5, only the elements necessary for understanding this exemplary embodiment are shown. Here, the control valve 11 is provided in a special holding element 52, which makes it possible to retrofit today's common fuel injection pump elements with the control valve designed according to the invention without any special rework on the pump side. It is essential when fastening the control valve 11 according to the invention in the holding element 52 that the holding force exerted on the control valve 11 is exerted in the longitudinal direction of the piston slide 12 in order to reliably avoid any deformation or tension of the high-pressure and low-pressure sealing gaps 28a and 28b. The holding element 52 has a stepped bore 43, into which the control valve 11 is inserted with the interposition of a sealing element 50. An end face of the control valve, which protrudes from the holding element 52, is provided with a thread onto which a nut 44 can be screwed, so that the control valve 11 is connected pressure-tight to the holding element 52 by a holding force oriented in the longitudinal direction of the piston valve 12. On the pump side, the holding element 52 has a connection part 45 which can be inserted into a connection bore 48 of the fuel injection pump 1. This connection bore 48 of the fuel injection pump 1 has the usual dimensions for receiving the pressure valve 9, so that the control valve 11 is mounted via the holding element 52 without reworking on the pump side. To fasten the holding element 52, the pump-side connecting part 45 is provided with a recess 46, into which preferably two ring-shaped pressing elements 47 are inserted. A fastening member 49 is screwed onto the thread of the connection bore 48, which is in operative connection with the pressing elements 47 and connects the holding element 52 pressure-tightly to the fuel injection pump 1 and thus to the pump chamber 6 via these pressing elements 47. A receiving space 51 for the pressure valve 9 is provided facing away from the fuel injection pump and is designed in a manner analogous to the receiving bore 48 of the fuel injection pump 1. It should be noted that the bore 43 of the holding element 52 is made with a slight oversize, in order to avoid any deformation or tensioning of the sealing gaps 28a and 28b on the low-pressure and high-pressure side resulting from the fastening of the pressure valve 9 in the receiving space 51.

Claims (25)

1. A fuel injection appliance for a compression- ignition internal combustion engine, the appliance comprising a pilot valve (11) arranged between a fuel injection pump (1) and an injection nozzle (10) and in the casing of which a valve member (16) constructed as a piston slide (12) is axially movable by an electromagnetic regulator (34), in which a high-pressure chamber (22) located in the casing is connected to a high-pressure duct (8) of the injection pump (1) and to the injection nozzle (10) while a low-pressure chamber (23) also located in the casing is connected to a low-pressure duct, preferably a discharge duct (15), in which the valve member (16) of the piston slide (12) interacts with a valve seat provided between the high-pressure chamber (22) and the low-pressure chamber (23), and in which the piston slide (12) is held by a spring (13) in the valve member's (16) closing position on the valve seat,
characterized in that the high-pressure section (17) of the piston slide (12) is of uniform diameter substantially equal to the outer diameter of the valve member's (16) sealing region which interacts with the valve seat, that the diameter of the piston slide's (12) low-pressure section (18) is smaller than that of its high-pressure section (17), and in that a second electromagnetic regulator (29) is provided the actuating member (31) of which strikes, after a pre-stroke path, the piston slide (12) and moves it into its opening position.
2. A fuel injection appliance according to claim 1, including two further chambers (20,21) arranged in the casing, one at each end face of the piston slide (12), and connected to one another by a duct (25),
characterized in that the piston slide's (12) end face disposed in the chamber (20) on the high-pressure side is larger than its end face disposed in the chamber (21) on the low-pressure side.
3. A fuel injection appliance according to claim 1 or claim 2,
characterized in that the spring (13) is arranged on the piston slide's (12) end face disposed on the high-pressure side.
4. A fuel injection appliance according to any of the preceding claims,
characterized in that both the electromagnetic regulators (34, 29) are arranged at the piston slide's (12) end face disposed on the low-pressure side.
5. A fuel injection appliance according to any of the preceding claims,
characterized in that the piston slide (12) is held in its open position by the second electromagnetic regulator (29).
6. A fuel injection appliance according to any of the claims 1 to 5,
characterized in that a spring (32) is secured to the actuating member (31) of the second regulator (29), and in that this spring is pretensioned when the coil of the second regulator (29) is energized.
7. A fuel injection appliance according to claim 6,
characterized in that a spacer (33) serving to limit the spring's (32) pretensioning is arranged on the actuating member (31) of the second regulator (29).
8. A fuel injection appliance eccording to any of the claims 1 to 7,
characterized in that the armature of the first electromagnetic regulator (34) is a two-part one comprising an inner and an outer armature part (35a, 35b), and in that the inner armature part (35a is axially movable in relation to the outer armature part (35b).
9. A fuel injection appliance according to claim 8,
characterized in that the inner and outer armature parts (35a, 35Q) are connectable as far as the axial movement is concerned.
10. A fuel injection appliance according to any of the claims 1 to 9,
characterized in that the first and second electromagnetic regulators (34, 29) including their respective armatures (31, 35a, 35b) and iron cores (30,36) are associated with the piston slide's (12) end face disposed on the low-pressure side, and in that the inner armature part (35a) of the first regulator (34) is in direct operative connection with the piston slide (12) while the armature (31) of the second regulator (29) is in indirect operative connection with the inner armature part (35a) of the regulator (34).
11. A fuel injection appliance according to claim 10,
characterized in that a stop (38) serving to limit the axial movement of the outer armature part (35b) of the first regulator (34) is arranged between the first and the second (34, 29).
12. A fuel injection appliance according to claim 7 and claim 11,
characterized in that the stop (38) and the spacer (33) of the actuating member (31) of the second regulator (29) are designed so as to form - when the piston slide (12) is in its closing position and the spring (32) is pretensioned to its maximum extent - the pre-stroke path between the inner armature part (35a) of the first regulator (34) and the actuating member (31) of the second regulator (29).
13. A fuel injection appliance according to any of the claims 10 to 12,
characterized in that a spacing element (41) is arranged between the iron core (36) and the outer armature part (35b) of the first regulator (34) and serves to limit the axial movement of the outer armature part (35b).
14. A fuel injection appliance according to any of the claims 10 to 13,
characterized in that another stop (27) is associated with the end face of the piston slide's high-pressure section (17).
15. A fuel injection appliance according to any of the claims 1 to 9,
characterized in that the second regulator (29) including its iron core (30) and armature (31) are associated with the piston slide's (12) end face disposed on the low-pressure side whilst the first regulator (34) including its armature parts (35a, 35b) and iron core (36) are associated with the piston slide's (12) end face disposed on the high-pressure side.
16. A fuel injection appliance according to claim 15,
characterized in that the armature (31) of the second regulator (29) is located directly opposite the piston slide (12) and is arranged to strike it, and in that the inner armature part (35a) of the first regulator (34) is fastened to the piston slide (12).
17. A fuel injection appliance according to claim 15 or claim 16,
characterized in that the iron core (36) of the first regulator (34) is provided with a shoulder (36a) which forms a spacing element and is associated with the inner armature part (35a).
18. A fuel injection appliance according to claim 15 or claim 17,
characterized in that the spacer 33 of the second regulator (29) is constructed so that, in the piston slide's (12) closing position, the armature (31) of the second regulator (29) is shifted into a position axially spaced from the piston slide (12).
19. A fuel injection appliance according to any of the claims 1 to 18,
characterized in that the fuel injection pump (1) includes a pump piston (3) rotatable about an axis extending in the pump piston's (3) longitudinal direction, and in that the pump piston is provided at its outer surface with a longitudinally extending groove (42) connectable to the pump chamber.
20. A fuel injection appliance according to claim 19,
characterized in that the pump piston (3) is arranged to be rotated by a mechanical regulating device controlled by the speed of the internal combustion engine, and in that the longitudinal groove (42) is thus arranged to be brought into communication with a suction duct (79).
21. A fuel injection appliance according to any of the claims 1 to 20,
characterized in that a sensor (40) is located in the ares in which one of the piston slide's (12) end faces or one of the armatures (31, 35a, 35b) is arranged to move, and in that the sensor, which includes a permanent magnet, pole shoes and an induction coil, generates - in dependence either on the piston slide's movement or on an air gap at one of the slide's (12) end faces - a pulse-like signal to initiate closing and/or opening of the pilot valve (11).
22. A fuel injection appliance according to any of the claims 1 to 21,
characterized in that the pilot valve (11) is arranged in a holder, which is connectable to the fuel injection pump and is secured to the holder by a holding force exerted in the longitudinal direction of the piston slide (12).
23. A fuel injection appliance according to claim 22,
characterized in that the holder (52) is provided with a stepped bore (43) for mounting the pilot valve (11) therein, and in that the pilot valve (11) is fastened to the holder (52) by a screw joint (44).
24. A fuel injection appliance according to claim 22 or claim 23,
characterized in that the holder (52) is provided at its side closest to the pump with a connecting part (45) having a recess (46) for inserting thereinto one or more contact-pressure elements (47), and in that the holder is arranged to be connected to the fuel injection pump (1) by a fastening member (49), which is screwed into a connecting bore (48) of the fuel injection pump (1) and which interacts with the contact-pressure elements (47).
25. A fuel injection appliance according to any of the claims 22 to 24,
characterized in that the holder (52) is provided with a further bore (51) for installing a delivery valve (9) therein.
EP83112959A 1983-01-25 1983-12-22 Fuel injection device for compression ignition internal combustion engines Expired EP0114375B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE3302294 1983-01-25
DE19833302294 DE3302294A1 (en) 1983-01-25 1983-01-25 Fuel injection device for air compressing, self-ignitioning internal combustion engines

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT83112959T AT40447T (en) 1983-01-25 1983-12-22 Fuel injection device for air compressing, self-ignitioning internal combustion engines.

Publications (3)

Publication Number Publication Date
EP0114375A2 EP0114375A2 (en) 1984-08-01
EP0114375A3 EP0114375A3 (en) 1986-02-05
EP0114375B1 true EP0114375B1 (en) 1989-01-25

Family

ID=6189096

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83112959A Expired EP0114375B1 (en) 1983-01-25 1983-12-22 Fuel injection device for compression ignition internal combustion engines

Country Status (8)

Country Link
US (1) US4619239A (en)
EP (1) EP0114375B1 (en)
JP (1) JPS59165859A (en)
AT (1) AT40447T (en)
CA (1) CA1208511A (en)
DE (1) DE3302294A1 (en)
ES (1) ES8500387A1 (en)
RU (1) RU1830109C (en)

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DE4212797A1 (en) * 1992-04-16 1993-10-21 Kloeckner Humboldt Deutz Ag High pressure seal for fuel injection device - has multi-sectional sealing elements to form axial gap with steps in control valve and pump bore
DE19721841A1 (en) * 1997-05-24 1998-09-03 Mtu Friedrichshafen Gmbh Fuel injection system for air compressing, self-igniting combustion engine

Also Published As

Publication number Publication date
CA1208511A1 (en)
ES529100A0 (en) 1984-10-01
RU1830109C (en) 1993-07-23
DE3302294A1 (en) 1984-07-26
JPS59165859A (en) 1984-09-19
ES529100D0 (en)
CA1208511A (en) 1986-07-29
US4619239A (en) 1986-10-28
EP0114375A3 (en) 1986-02-05
AT40447T (en) 1989-02-15
ES8500387A1 (en) 1984-10-01
EP0114375A2 (en) 1984-08-01

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