EP0733798A2 - Dispositif d'injection de combustible suivant le principe de l'accumulateur d'énergie solide, pour moteurs à combustion interne - Google Patents

Dispositif d'injection de combustible suivant le principe de l'accumulateur d'énergie solide, pour moteurs à combustion interne Download PDF

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Publication number
EP0733798A2
EP0733798A2 EP96109438A EP96109438A EP0733798A2 EP 0733798 A2 EP0733798 A2 EP 0733798A2 EP 96109438 A EP96109438 A EP 96109438A EP 96109438 A EP96109438 A EP 96109438A EP 0733798 A2 EP0733798 A2 EP 0733798A2
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EP
European Patent Office
Prior art keywords
valve
bore
cylinder
interior
tappet
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
EP96109438A
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German (de)
English (en)
Other versions
EP0733798B1 (fr
EP0733798A3 (fr
Inventor
Wolfgang Dr. Heimberg
Wolfram Hellmich
Pau Malatinszky
Franz Kögl
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Ficht GmbH and Co KG
Original Assignee
Ficht GmbH
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Publication date
Priority claimed from DE4206817A external-priority patent/DE4206817C2/de
Application filed by Ficht GmbH filed Critical Ficht GmbH
Publication of EP0733798A2 publication Critical patent/EP0733798A2/fr
Publication of EP0733798A3 publication Critical patent/EP0733798A3/fr
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Publication of EP0733798B1 publication Critical patent/EP0733798B1/fr
Anticipated expiration legal-status Critical
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    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/462—Arrangement of fuel conduits, e.g. with valves for maintaining pressure in the pipes after the engine being shut-down
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/02—Pressure lubrication using lubricating pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D33/00—Controlling delivery of fuel or combustion-air, not otherwise provided for
    • F02D33/003—Controlling the feeding of liquid fuel from storage containers to carburettors or fuel-injection apparatus ; Failure or leakage prevention; Diagnosis or detection of failure; Arrangement of sensors in the fuel system; Electric wiring; Electrostatic discharge
    • F02D33/006—Controlling the feeding of liquid fuel from storage containers to carburettors or fuel-injection apparatus ; Failure or leakage prevention; Diagnosis or detection of failure; Arrangement of sensors in the fuel system; Electric wiring; Electrostatic discharge depending on engine operating conditions, e.g. start, stop or ambient conditions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047—Layout or arrangement of systems for feeding fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/08—Feeding by means of driven pumps electrically driven
    • 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
    • F02M39/00—Arrangements of fuel-injection apparatus with respect to engines; Pump drives adapted to such arrangements
    • F02M39/005—Arrangements of fuel feed-pumps with respect to fuel injection apparatus
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/04—Pumps peculiar thereto
    • 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
    • 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
    • F02M55/007—Venting means
    • 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
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • 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
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/027—Injectors structurally combined with fuel-injection pumps characterised by the pump drive electric
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/38—Pumps characterised by adaptations to special uses or conditions
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/047—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves being formed by deformable nozzle parts, e.g. flexible plates or discs with fuel discharge orifices
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow
    • 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
    • F02M63/06—Use of pressure wave generated by fuel inertia to open injection 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/16—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors
    • F02M69/18—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors the means being metering valves throttling fuel passages to injectors or by-pass valves throttling overflow passages, the metering valves being actuated by a device responsive to the engine working parameters, e.g. engine load, speed, temperature or quantity of air
    • F02M69/24—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for metering continuous fuel flow to injectors or means for varying fuel pressure upstream of continuously or intermittently operated injectors the means being metering valves throttling fuel passages to injectors or by-pass valves throttling overflow passages, the metering valves being actuated by a device responsive to the engine working parameters, e.g. engine load, speed, temperature or quantity of air the device comprising a member for transmitting the movement of the air throttle valve actuated by the operator to the valves controlling fuel passages
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/30—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for facilitating the starting-up or idling of engines or by means for enriching fuel charge, e.g. below operational temperatures or upon high power demand of engines
    • F02M69/34—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by means for facilitating the starting-up or idling of engines or by means for enriching fuel charge, e.g. below operational temperatures or upon high power demand of engines with an auxiliary fuel circuit supplying fuel to the engine, e.g. with the fuel pump outlet being directly connected to injection nozzles
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
    • F02D2041/2058—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit using information of the actual current value
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/2068—Output circuits, e.g. for controlling currents in command coils characterised by the circuit design or special circuit elements
    • F02D2041/2075—Type of transistors or particular use thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/08—Feeding by means of driven pumps electrically driven
    • F02M2037/085—Electric circuits therefor
    • 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
    • F02M2200/24—Fuel-injection apparatus with sensors
    • 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
    • F02M2200/40—Fuel-injection apparatus with fuel accumulators, e.g. a fuel injector having an integrated fuel accumulator

Definitions

  • the invention relates to a device for injecting fuel for internal combustion engines of the type specified in the preamble of claim 1.
  • Injection devices whose electrically operated reciprocating pumps operate according to the so-called solid-state energy storage principle, have a delivery piston or cylinder which is accelerated in a certain way almost without resistance, fuel being generally moved before the delivery pressure which builds up to Spraying the fuel through the injector is required. In this way, kinetic energy is absorbed or stored before the actual pressure build-up required for injection, which is then suddenly converted into a pressure increase in the fuel.
  • the fuel delivery chamber accommodating the delivery piston of the injection pump has, in a first section, axially parallel grooves in the inner wall through which Fuel can flow to the rear of the delivery piston if the delivery piston starts to move without any noticeable pressure build-up in the fuel.
  • the adjoining second section of the fuel delivery chamber is the actual pressure chamber, which has no grooves. If the accelerated delivery piston enters this pressure chamber, it is suddenly braked by the incompressible fuel, whereby the stored kinetic energy is converted into a pressure surge, through which the resistance of the injection valve is overcome, so that fuel is sprayed off.
  • the disadvantage here is that when the delivery plunger is immersed in the second section of the delivery space, because of unfavorable gap conditions, namely a relatively large gap width and a relatively small gap length, noticeably high pressure losses occur, which in particular reduce the possible speed and pressure level of the pressure build-up and thus make the spraying process unfavorable influence.
  • the pressure losses are caused by fuel flowing out of the pressure chamber into the pressure antechamber (first section of the fuel delivery chamber).
  • this disadvantage is to be avoided by mounting an impact body in the pressure chamber of the delivery cylinder on which the piston accelerates almost without resistance, so that the pressure loss during pressure build-up due to a relatively large gap length despite a relatively large gap width (large manufacturing tolerances ) between the impact body and the pressure chamber inner wall area can be kept reasonably small.
  • the disadvantage here is that the impacting process leads to a high level of wear on the bodies that meet.
  • the impact body is set into longitudinal vibrations by the impact, which are transferred to the fuel and disrupt the injection process there as high-frequency pressure vibrations.
  • a particular disadvantage of these known solid-state energy storage injection devices is that the injection process can be controlled only to a very limited extent, that is to say it can only be adapted to the load conditions of the engine to a very limited extent.
  • the reciprocating piston pump has a sleeve-shaped pump cylinder as a movable pump member, which is arranged in a longitudinally displaceable manner on a pump piston fixed in the pump housing and limits the pump pressure space, which is connected to the injection valve device via a longitudinal bore in the pump piston.
  • a cross hole in the pump cylinder allows fuel to flow to the back of the cylinder when storing energy. Passing over the front edge of the piston with the bore leads to pressure build-up and thus to fuel spraying. In this case, too, high gap losses occur when the pressure builds up.
  • the object of the invention is to provide a cost-effective, easy-to-manufacture device for injecting fuel of the type mentioned at the outset, with which wear-free fuel can be injected without any noticeable pressure losses when building up pressure, and fuel can be precisely controlled depending on the load, and which is particularly suitable for high-speed internal combustion engines.
  • the fuel injection device has a reciprocating pump in which a valve is integrated which interrupts the acceleration without resistance, so that a pressure surge is generated with which fuel is sprayed off.
  • the valve is arranged outside the leading liquid-tight contact area between a reciprocating piston element and a reciprocating piston cylinder of the reciprocating pump, so that pressure build-up can be carried out without wear and tear without noticeable pressure losses, fuel-sprayable being controllable depending on the load and the entire device being of a very simple design.
  • FIG. 1 shows a compact design of the electrically operated reciprocating piston pump according to the invention with an integrated stop valve.
  • a coil 201 is arranged in a cylindrical multi-part housing 200 in an inner space 202 delimited by an outer jacket 200a and a cylindrical inner jacket 200b as well as an end wall 200c on the tank side and an end wall 200d on the pressure line side.
  • the cylindrical interior 202 of the housing 200 which is surrounded by the inner jacket 200b, is divided by a radially inwardly extending ring 203 into an interior region on the tank side and a pressure line side.
  • an annular bead 204 of a piston 205 is seated positively and firmly in this interior space against the ring edge of the ring 203, the piston 205 reaching through the ring opening 206 of the ring 203 at a distance and projecting into the tank-side area of the interior 202.
  • the piston 205 is penetrated by a through bore 207, which is designed to be enlarged in the tank-side end region of the piston and supports a valve 208 there, which is pressed against the valve seat 209a by a coil spring 209 in the direction of the tank side for the closed position, with the action a pressure acting from the tank side can be opened.
  • a pump cylinder 210 of the reciprocating piston pump is seated in a form-fitting and slidable manner an annular step 213 is pressed in the inner space 202, one projecting beyond the end face 214 Valve socket 215 protrudes a bit at a radial distance into the interior space 202a, which is radially narrowed in this area, and the end ring surface of the cylinder 210 on the pressure line side is arranged at a distance from the ring 203, thus creating a movement space for the cylinder 210.
  • the cylinder 210 seated in a form-fitting manner on the inner wall of the interior 202 has axially parallel, frontally open longitudinal grooves 216 in the lateral surface, the function of which is explained below.
  • the through bore 217 penetrating the pump cylinder 210 and receiving the piston 205 supports a tappet valve arranged in front of the piston 205 on the tank side, the tappet plate 218 of which is arranged in a short bore extension at a distance from the end face of the piston 205 and the tappet stem 219 of the narrowed bore 217a in the valve stub 215, supporting itself against the inner wall of the bore 217a, reaches through and projects into the narrowed interior 202a.
  • a plate 220 is expediently fastened, which has holes 221, the function of which is explained further below, the plunger stem 219 projecting a little further from the plate 220 and abutting the tank-side bottom surface 222 of the interior 202a.
  • the plunger stem 219 is chosen so long that the plunger plate 218 is lifted from its valve seat, the pressure line side opening 223 of the narrowed bore 217a, so that a certain gap "X" is formed, the meaning and purpose of which is explained below.
  • a helical spring 224 stabilizes this position of the tappet valve in the illustrated rest position of the reciprocating pump, in which the spring 224 is supported at one end on the end face 214 of the cylinder 210 and at the other end against the plate 220.
  • axially parallel bores 225 extend into the bottom wall and open into an axial valve chamber 226, in which a valve plate 229, which is pressed against a valve seat 227 by a coil spring 228 in the tank direction, is arranged, the grooves 230 which can be covered peripherally by the valve seat 227 has, so that the valve can be opened by a tank connection-side pressure against the load of the spring 228 and a passage from the valve chamber 226 to the bores 225 is created.
  • the valve chamber 226 is connected to a fuel line leading to the fuel tank (not shown);
  • a pressure line (not shown) is attached to the end wall 200d on the pressure line side or to an extended connecting piece of the inner wall 200b, which leads to the spray valve.
  • the arrows drawn in FIG. 13 indicate the path of the fuel.
  • the reciprocating pump shown in Figure 1 works as follows.
  • the excitation of the coil 201 accelerates the cylinder 210 from the rest position shown in the direction of the pressure line almost without resistance, fuel flowing out of the space 202 via the grooves 216 and out of the bore 217 or the plunger plate space in the direction of the interior 202a.
  • the accelerated movement ends abruptly when the valve seat 223 hits the valve plate 218, so that the stored energy of the cylinder 210 is transferred to the fuel located in the plunger antechamber.
  • the valve 208 is opened and the pressure on the fuel in the bore 207 or in the pressure line is propagated, as a result of which fuel is sprayed off through the injection nozzle.
  • the excitation is not yet switched off, fuel is sprayed off as long as the cylinder is moved.
  • the tappet valve 218, 219 is entrained by the cylinder 210 and there is a negative pressure in the interior spaces 202, 202a and in the bores 225 and the antechamber of the valve space 226 delimited by the valve 229, so that the valve 229 is opened.
  • the fuel flows through the peripheral grooves 230 in the valve plate 229, the antechamber of the valve chamber 226, the bores 225 and the holes 221 in the plate 220 into the interior 202a and via the grooves 216 into the interior 202.
  • the spring 211 After the excitation has been switched off the spring 211 returns the cylinder to its rest or home position pushed back, previously the plunger stem 219 abuts against the bottom wall 222 and the plunger valve is opened so that fuel can flow through the gap between the plunger stem and the bore 217a into the plunger plate antechamber 217.
  • the valve 208 remains closed. It acts as a stand pressure valve and maintains a stand pressure in the fuel in the space between the injection valve (not shown) and the valve plate 208, which is, for example, higher than the vapor pressure of the liquid at the maximum occurring temperature, so that bubbles are prevented can.
  • the piston 205 is formed in one piece with the end wall 200d and the standing pressure valve 208, 209, which is in a pipe socket 208a is housed, covers the pressure line side mouth of the bore 207 going through the piston 205.
  • the sliding pump cylinder 210 which acts as an anchor, is constructed in several parts for a simple possibility of mounting the valve tappet 218, 219. Since the multiple parts are not essential to the invention, the structure of the cylinder 210 is not described in detail.
  • the tappet stem 219 is made relatively short and can only protrude over the valve-side end ring surface 214 of the cylinder 210.
  • the end ring surface 214 abuts in the region of the end wall 200c against a plastic block 231 mounted there, which has through bores 232 which open peripherally in grooves 233 which are connected to the tank-side interior 202, with bores 234 from the tank-side interior 202 to the enlarged bore region of the bore Guide 217 in cylinder 210.
  • the bores 232 open into the axial valve space 226 leading to the tank, which is accommodated in a pipe socket 226a.
  • the tappet valve 218, 219 is not spring-loaded. It works due to inertial forces, with the plunger stem sitting approximately form-fit in the narrowed bore 217a.
  • the tappet valve In the position shown in FIG. 2, the tappet valve is pressed against the plastic block 231 by the pressure acting on the tappet plate 218 in the spaces 202, 217, 207. If the cylinder 210 is accelerated, the tappet valve remains in this position until it is carried along by the valve seat 223. During the return movement of the armature cylinder 210, the tappet stem 219 abuts against the plastic block 231, so that the tappet valve returns to the starting position shown.
  • the bore extension of the bore 217, in which the tappet plate 218 is received forms an annular step 235 on the pressure line side, which in the rest position of the tappet valve is located only a short distance in front of the tappet plate 218 and against which the tappet plate 218 abuts when the tappet is due to inertia the return movement of the cylinder 210 lifts off the valve seat and / or the valve should be rebounded from the plastic block 231 during the return movement of the cylinder 210.
  • In the end face of the ring step 235 there are recesses 235a which ensure an unimpeded flow of the fuel. In this way, the rest position of the tappet valve is ensured with simple means.
  • the end ring surface 214 is arranged at a small distance "A" from the surface of the plastic block 231 (FIG. 15).
  • Support webs 214a which protrude from the end ring surface 214, lie against the surface of the plastic block 231 and provide the distance "A", so that there is no disturbing negative pressure effect when the anchor cylinder 210 is started between the end ring surface 214 and the surface of the plastic block 231 can.
  • Such support webs can be arranged for the same purpose on the end face of the plunger stem 219 (not shown).
  • the distance "A" is chosen so small that during the return stroke, damping takes place by squeezing fuel out of the gap "A".
  • the embodiment of the reciprocating piston pump according to FIGS. 2 and 3 can be provided with a simply constructed, effective armature damping device, which is shown in FIG. 4.
  • the tappet stem 219 has in its free end region a flange ring 219a, which overlaps the end ring surface 214 a little laterally and can rest against the end ring surface 214.
  • a recess 231a corresponding to the flange ring 219a is made, into which the flange ring 219a fits approximately in a form-fitting manner, so that a piston-cylinder-like hydraulic damping device is formed.
  • the flange ring 219a is carried along by the end face surface 214. As soon as the flange ring 219a dips into the recess 231a, fuel is displaced therefrom and the armature cylinder 210 is braked. When the armature cylinder 210 accelerates, the armature cylinder moves almost without resistance. The flange ring 219a and thus the tappet valve 218, 219 initially remain in the recess 231a until the tappet valve is carried along by the valve seat.
  • the thickness of the flange ring 219a is expediently made somewhat larger than the depth of the recess 231a, so that the The end ring surface 214 remains in the rest position of the armature cylinder 210 at a distance from the surface of the plastic block 231 and support webs are not required in this respect.
  • a bore 236 is expediently arranged in the pressure line-side end wall 200d, which leads outwards from the pressure line-side interior 202 and on which a nozzle 237 with a through-bore 238 is placed on the outside.
  • fuel is pumped out of the armature cylinder 210, so that the pump and / or the fuel supply line can be flushed out of air bubbles.
  • fuel can also be flushed during the injection activity of the pump, thereby dissipating heat, and preventing the formation of bubbles.
  • the spring is compressed.
  • the spring 238 releases its stored spring force to the armature cylinder 210, so that the latter moves correspondingly accelerated into the rest position.
  • the cylinder 210 acts as a piston-like anchor element which is guided in the inner cylinder 200b in a liquid-tight manner.
  • FIG. 5 An injection pump 1 similar to the injection pump shown in FIG. 1 is shown in FIG. 5, the same parts being assigned the same reference numbers.
  • the piston 205a which is partially seated in the armature cylinder bore 217, is not fastened to the end wall 200d on the pressure line side, but is mounted so as to be axially movable and is part of the spray valve device 3.
  • the injection valve 3 has a valve cap 3b which fits into the front wall 200d of the housing 200 in the injector side Interior 202 is screwed gripping.
  • the valve cap has a central injection nozzle hole 3d.
  • the piston 205a covers the injection nozzle bore 3a with an end face 205b with a reduced diameter.
  • the reduced surface area 205b merges with a truncated cone 205c into the cylindrical part of the piston 205a.
  • the piston 205a is pressed in the armature cylinder bore 217 by a compression spring 240 against the injection nozzle bore 3d, the compression spring 240 being supported against an intermediate wall 241 arranged in the armature cylinder bore 217, which divides the bore 217 into an injection nozzle-side and a tank-side region .
  • At least one bore 242 leads from the end ring surface 212 through the armature cylinder 210 into the enlarged cylinder bore space of the tank-side region of the bore 217, in which the tappet plate 218 is received, and a bore 243 through the armature cylinder 210 from the region of the bore 217 in the injector side the tank-side interior 202, the central region of the armature cylinder 210 being positively and almost liquid-tightly seated on the inner wall of the interior 202.
  • the armature cylinder preferably has grooves in the tank-side region of the interior 202, the groove webs abutting the inner wall of the interior 202 and forming guides for the armature cylinder 210 there.
  • the pressure surge is transmitted to the conical surface of the truncated cone 205c and lifts the piston 205 against the pressure of the spring 240 from the nozzle 3a, so that fuel is hosed.
  • a vacuum is created in the space 202a and in the tank-side interior 202, which also acts on the piston 205, but which is very much less than the spring force of the spring 240, so that the piston remains unaffected.
  • the negative pressure opens the valve 229, so that fuel is sucked in.
  • the valve 229 closes again due to the spring force of the spring 228 when the return movement of the armature cylinder 210 begins, so that fuel is then forced into the spaces of the bore 217 and the interior 202 by the armature-cylinder movement.
  • the function of the valve 292 corresponds to the function of the same valve 229 in the embodiment of the injection pump 1 according to FIG. 13.
  • FIG. 6 A further embodiment of the injection pump 1 according to the invention, in which the injection nozzle 3 is accommodated directly in the end wall 200d in the housing 200 of the injection pump 1, results from FIG. 6. This embodiment is similar to that of FIG. 5, which is why the same parts have the same reference numbers Marked are.
  • valve cap 3b forms a valve seat 3c for a tappet valve 244, the valve plate 245 of which is pulled from the outside against the valve seat 3c, and the tappet stem 246 of which engages freely through the cap bore 3d following the valve seat 3c or is supported radially by ribs 247 and freely through the Armature cylinder bore 217 goes and ends shortly before the enlarged area of the bore 217, in which the tappet plate 218 of the tappet valve 218, 219 is received.
  • a ring 248a having holes or edge recess 248 is fastened, against which the injector side is located supports a compression spring 250, which rests against the end wall 200d of the housing 200 or against the valve cap 3b. It is important in this embodiment that the anchor cylinder 210 only has the through hole 217 and no marginal grooves, but rests positively on the inner wall of the interior 202.
  • this injection pump which has no separate piston, functions as follows. If the tappet valve 218, 219 is taken away from the valve seat of the armature cylinder 210, the sudden pressure build-up in the fuel takes place in the space 202, 217 and 3d, so that the tappet valve 244 opens for spraying against the pressure of the return spring 250. Then, after another stroke "H", the plunger plate 218 hits the plunger stem 246 and keeps the valve 244 open.
  • FIG. 7 An embodiment of the injection pump 1 according to the invention which is similar to the embodiment shown in FIG. 6 is shown in FIG. 7, the same parts again being designated with the same reference numbers.
  • the tappet stem 246 of the tappet valve 244 is made shorter and, in the rest position or starting position of the pump 1, extends only into the end region of the armature cylinder bore 217 on the injection valve side. Accordingly, the return spring 250 is also shortened. In addition, however, a further compression spring 251 presses against the ring 248a from the tank side, which is supported at one end against a wall 217e having a central bore 217d, which divides the bore 217 into an injector-side and a tank-side region which communicate via the bore 217d stand.
  • the spring 251 supports the opening of the valve 244 as in the case of the embodiment according to FIG. 6, in which the opening is supported by the valve disk 218, which strikes the tappet stem 246. The springs then also hold valve 244 in the open position, as long as the spring pressure of the spring 250 or 251 causes this.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Steroid Compounds (AREA)
EP96109438A 1992-03-04 1993-03-04 Dispositif d'injection de combustible suivant le principe de l'accumulateur d'énergie solide, pour moteurs à combustion interne Expired - Lifetime EP0733798B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4206817 1992-03-04
DE4206817A DE4206817C2 (de) 1991-10-07 1992-03-04 Kraftstoff-Einspritzvorrichtung nach dem Festkörper-Energiespeicher-Prinzip für Brennkraftmaschinen
EP93905299A EP0629265B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de carburant fonctionnant selon le principe de l'accumulateur d'energie a solide pour moteurs a combustion interne

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP93905299.9 Division 1993-03-04
EP93905299A Division EP0629265B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de carburant fonctionnant selon le principe de l'accumulateur d'energie a solide pour moteurs a combustion interne

Publications (3)

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EP0733798A2 true EP0733798A2 (fr) 1996-09-25
EP0733798A3 EP0733798A3 (fr) 1996-12-11
EP0733798B1 EP0733798B1 (fr) 2000-06-07

Family

ID=6453209

Family Applications (5)

Application Number Title Priority Date Filing Date
EP93905295A Expired - Lifetime EP0630442B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de carburant fonctionnant selon le principe de l'accumulateur d'energie a solide, pour moteurs a combustion interne
EP93905298A Expired - Lifetime EP0629264B1 (fr) 1992-03-04 1993-03-04 Pompe a piston alternatif
EP96109438A Expired - Lifetime EP0733798B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de combustible suivant le principe de l'accumulateur d'énergie solide, pour moteurs à combustion interne
EP96101218A Expired - Lifetime EP0725215B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de combustible suivant le principe de l'accumulateur d'énergie solide, pour moteurs à combustion interne
EP93905299A Expired - Lifetime EP0629265B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de carburant fonctionnant selon le principe de l'accumulateur d'energie a solide pour moteurs a combustion interne

Family Applications Before (2)

Application Number Title Priority Date Filing Date
EP93905295A Expired - Lifetime EP0630442B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de carburant fonctionnant selon le principe de l'accumulateur d'energie a solide, pour moteurs a combustion interne
EP93905298A Expired - Lifetime EP0629264B1 (fr) 1992-03-04 1993-03-04 Pompe a piston alternatif

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP96101218A Expired - Lifetime EP0725215B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de combustible suivant le principe de l'accumulateur d'énergie solide, pour moteurs à combustion interne
EP93905299A Expired - Lifetime EP0629265B1 (fr) 1992-03-04 1993-03-04 Dispositif d'injection de carburant fonctionnant selon le principe de l'accumulateur d'energie a solide pour moteurs a combustion interne

Country Status (9)

Country Link
US (3) US5520154A (fr)
EP (5) EP0630442B1 (fr)
JP (8) JP2626678B2 (fr)
AT (5) ATE140768T1 (fr)
AU (5) AU664739B2 (fr)
CA (3) CA2127800C (fr)
DE (5) DE59304903D1 (fr)
HK (1) HK1013676A1 (fr)
WO (3) WO1993018297A1 (fr)

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JP3330544B2 (ja) 2002-09-30
AU3790995A (en) 1996-03-07
US5520154A (en) 1996-05-28
JP2626677B2 (ja) 1997-07-02
JPH09170519A (ja) 1997-06-30
WO1993018297A1 (fr) 1993-09-16
AU679648B2 (en) 1997-07-03
AU681827B2 (en) 1997-09-04
AU3630593A (en) 1993-10-05
DE59310057D1 (de) 2000-07-13
CA2127800A1 (fr) 1993-09-16
WO1993018296A1 (fr) 1993-09-16
CA2127799A1 (fr) 1993-09-16
JP2867334B2 (ja) 1999-03-08
AU667345B2 (en) 1996-03-21
JPH09177636A (ja) 1997-07-11
EP0629265B1 (fr) 1997-06-04
JP2002089413A (ja) 2002-03-27
EP0725215B1 (fr) 1998-08-05
ATE154100T1 (de) 1997-06-15
EP0630442B1 (fr) 1996-12-27
EP0629265A1 (fr) 1994-12-21
ATE193753T1 (de) 2000-06-15
WO1993018290A1 (fr) 1993-09-16
DE59304903D1 (de) 1997-02-06
JPH11107883A (ja) 1999-04-20
JPH11101169A (ja) 1999-04-13
EP0629264A1 (fr) 1994-12-21
ATE146851T1 (de) 1997-01-15
EP0725215A2 (fr) 1996-08-07
CA2127801C (fr) 1999-06-15
CA2127799C (fr) 1999-06-29
EP0629264B1 (fr) 1996-07-24
AU3630793A (en) 1993-10-05
JPH07504476A (ja) 1995-05-18
JP2626678B2 (ja) 1997-07-02
JPH07504954A (ja) 1995-06-01
AU5627396A (en) 1996-10-03
DE59308851D1 (de) 1998-09-10
JP3282711B2 (ja) 2002-05-20
EP0733798B1 (fr) 2000-06-07
CA2127800C (fr) 1999-06-29
JPH07504475A (ja) 1995-05-18
HK1013676A1 (en) 1999-09-03
DE59306679D1 (de) 1997-07-10
EP0725215A3 (fr) 1996-08-21
EP0733798A3 (fr) 1996-12-11
US5469828A (en) 1995-11-28
EP0630442A1 (fr) 1994-12-28
US6188561B1 (en) 2001-02-13
DE59303326D1 (de) 1996-08-29
AU671100B2 (en) 1996-08-15
AU664739B2 (en) 1995-11-30
CA2127801A1 (fr) 1993-09-16
AU3630893A (en) 1993-10-05
ATE169376T1 (de) 1998-08-15
ATE140768T1 (de) 1996-08-15

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