EP0282508A1 - Dispositif d'injection de carburant dans un moteur diesel avec preinjection. - Google Patents

Dispositif d'injection de carburant dans un moteur diesel avec preinjection.

Info

Publication number
EP0282508A1
EP0282508A1 EP87905421A EP87905421A EP0282508A1 EP 0282508 A1 EP0282508 A1 EP 0282508A1 EP 87905421 A EP87905421 A EP 87905421A EP 87905421 A EP87905421 A EP 87905421A EP 0282508 A1 EP0282508 A1 EP 0282508A1
Authority
EP
European Patent Office
Prior art keywords
piston
line
slide
valve
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
EP87905421A
Other languages
German (de)
English (en)
Other versions
EP0282508B1 (fr
Inventor
Peter Fuchs
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.)
MAN B&W Diesel AS
Original Assignee
Nova Werke 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 Nova Werke AG filed Critical Nova Werke AG
Priority to AT87905421T priority Critical patent/ATE61449T1/de
Publication of EP0282508A1 publication Critical patent/EP0282508A1/fr
Application granted granted Critical
Publication of EP0282508B1 publication Critical patent/EP0282508B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—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
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/105—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive hydraulic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • the invention relates to a fuel injection device for a diesel internal combustion engine, in each of which an injection nozzle is connected to a fuel pump via a pressure line, the fuel pump has a cylinder with at least one fuel line for the inflow and outflow of fuel and a pump chamber, and a pump piston the pump piston has at least one annular space connected to the pump space with two control edges and the cylinder has an associated relief bore for interrupting the pressure build-up in the pump space.
  • Fuel injection devices of this type are used in internal combustion engines in which the main injection phase is preceded by a pre-injection. As is known, this allows the load on the engine components to be reduced and the combustion process in the internal combustion engine to be improved.
  • Such an injection device is known from US Pat. No. 4,426,198, this device having a piston with an oblique control edge and being driven by a camshaft.
  • the pump housing is provided in a known manner with a fuel chamber, into which inlet bores for the fuel open, and from which a pressure line to the injection nozzle originates.
  • the end face of the pump piston and the edges of an annular space on the piston skirt form control edges and interact in a known manner with the inlet bores.
  • a second annular space is arranged below the first annular space with the sloping edge, which is connected to the fuel chamber.
  • This annular space is also connected to the fuel chamber of the pump, ie the pump space.
  • a relief bore is arranged in the pump housing and is connected to the drain line for the fuel.
  • the inflow lines for the fuel and the relief bore are closed by the piston and pressure is built up in the pump chamber. This pressure is released again as soon as the lower annulus clears the relief bore, which also interrupts the injection process.
  • the duration of the interruption depends on the dimensions of the second annular space and the speed of the upward movement of the piston. The interruption takes place at a point in time at which the piston already has a relatively high speed.
  • the pump chamber can drain displaced fuel
  • Annulus and the relief bore have relatively large dimensions, which leads to increased leakage.
  • the object of the invention is to create a fuel injection device which, instead of the mechanical camshaft drive, enables the use of a drive acted upon by pressure medium, and in which the piston speed is reduced during the interruption phase and the overall stroke of the pump piston is increased and at the same time the injection pressure can be increased. Furthermore, the device is intended to enable the precise interruption of the injection phase even with fast-running engines and to allow the pre-injection, the interruption and the main injection phase to be changed as a function of the operating state. The device should also have a mechanical emergency running device.
  • the device for solving these tasks is characterized in that the pump piston is connected to a drive unit which is independent of the fuel system and is operated with a pressure medium, this drive unit is an axial piston unit, a pressure source and a mechanically and / or electrically switchable first control device with a Main slide and an auxiliary slide, main and auxiliary slide each have a return piston, which are connected to the pump chamber via a line and acted upon by fuel, in the fuel line on the pump a second control device with an overflow / suction valve and at least one interruption valve is arranged, and the overflow / suction valve has a switching piston unit, the piston chamber of which is connected via a first line to the relief bore on the pump cylinder and the pump chamber and via a second line to the interrupter valve and then to the fuel line is.
  • the drive unit acted upon by a pressure medium has a first control device with a main and auxiliary slide, which regulates the inflow and outflow of pressure medium to the axial piston unit.
  • This pressure medium system is separate from the fuel system and allows the use of particularly suitable pressure media, such as high pressure hydraulic oil.
  • the fuel system of the fuel pump and the pressure medium system of the axial piston unit are independent systems, which are linked to one another only via the return pistons of the first control device.
  • the main and auxiliary slides of the first control device have return pistons which are connected to the pump chamber and acted upon by fuel. This connecting line from the pump chamber to the reset piston of the control device enables the pressure medium system to be directly influenced by the fuel system.
  • the first control device is acted upon by fuel under high pressure at a desired point in time and the pressure medium system of the axial piston unit is controlled.
  • the second control device arranged in the fuel system allows the control of the inflow and outflow of fuel and, at the same time, the influencing of the first control device as a function of the pressure in the pump chamber.
  • This arrangement has the advantage that the phases of the injection process are controlled directly with the aid of the fuel pressure and the piston movement.
  • the relief bores in the pump cylinder only serve to transmit pressure surges and the device therefore permits very high piston speeds and the use of all types of fuel.
  • the length of the interruption phase can be changed during the injection phase by means of the interruption valve on the second control device.
  • a preferred embodiment of the invention is characterized in that the cylinder of the pump in the upper loading If at least one fuel feed line to the pump chamber and in the piston movement area has a first relief bore and a second relief bore arranged below the first, these relief bores are part of the lines between the pump chamber and the return piston and the switching piston unit, and three annular spaces on the jacket of the pump piston arranged with two control edges and connected to the pump chamber via a channel.
  • a connecting line with a check valve is arranged between the piston space of the reset piston on the auxiliary slide and the piston space of the reset piston on the main slide, and the piston space of the reset piston on the auxiliary slide is connected to the piston space of the switching piston via a further line Control device connected.
  • Control edges on the pump piston and two relief bores on the pump cylinder enable the main and auxiliary spool on the first control device to be actuated correctly ; trustee 'device and the switching points in the second control device. Additional interruptions in the injection phase can be achieved by arranging further annular spaces with control edges.
  • the relief bore and the annular spaces serve only to transmit pressure surges and, since the flow rates are very small, can have small dimensions.
  • the main slide has three annular spaces separated by locking seats and two interconnected slide bodies and the auxiliary slide two by one
  • Locking seat separate annular spaces and a slide body, a connecting line being arranged between the central annular space of the main slide and one of the annular spaces of the auxiliary slide, a pressure line and a return line leading to each of the other annular spaces of the main slide, and the second annular space of the Auxiliary slide is connected to the axial piston unit via a line.
  • a further improvement in the fuel injection device can be achieved in that, in a first switching position of the main slide, a slide body blocks the pressure line and the return line is connected to the connecting line to one of the annular spaces of the auxiliary slide, and in a second switching position the other slide ⁇ body blocks the return line and the pressure line is connected to the connecting line to the auxiliary slide.
  • the slide body of the auxiliary slide expediently has a throttle bore, and this throttle bore connects the two annular spaces to one another when the locking seat is closed.
  • a preferred embodiment of the invention is characterized in that in a first switching position of the auxiliary slide, the slide body releases the locking seat and the line to the axial piston unit is connected directly to the connecting line to the main slide, and in a second switching position the slide body blocks the line to the axial piston unit and forms a restricted flow channel via the throttle bore between the two annular spaces.
  • the full volume flows to the axial piston unit and moves the piston at normal speed.
  • the auxiliary slide takes up the second switching position when the first annular space on the pump piston interacts with the first relief bore on the pump cylinder.
  • the fuel under pressure moves the auxiliary slide over the return piston.
  • the throttle bore arranged in the slide body of the auxiliary slide only allows a reduced volume flow from the pressure medium source to the axial piston unit.
  • the speed of movement of the pump piston is reduced, the reduction being controllable by changing the cross section of the throttle. From this follows the advantage that practical during the interruption phase of the injection no stroke volume or working distance of the pump piston is lost.
  • the second control unit has two interrupter valves, both valves are each provided with a control piston, a connecting line is present between the valve chamber of one of the interrupter valves and the piston chamber of this interrupter valve, and an auxiliary valve in this connecting line is arranged. Furthermore, the piston chamber of the second interrupter valve is connected via a line to the lower relief bore on the pump cylinder, and a spring opens the valve in the depressurized state.
  • the second interrupter valve is preferably provided with a spindle led out of the control unit.
  • the piston of the auxiliary valve is loaded by a spring and the valve is open in the depressurized state, the piston chamber being connected via a line to the connecting line between the main and auxiliary spool and a switching valve with a connection to the return line being installed in this line is.
  • the two interrupter valves are connected to the fuel system and the pump chamber via lines and are controlled by pressure surges. These two valves are switched so that one is normally open and the other is closed. This arrangement permits very fast switching operations, since the one interrupter valve can already be closed during the opening movement and vice versa. In addition, the second control unit and the pump remain functional even if the control elements fail.
  • the interrupter valves can also be controlled indirectly mechanically or electrically.
  • the direct hydraulic control has the advantage that no additional switching media are necessary and the external influences on the control are thereby reduced.
  • the switching valve which controls the auxiliary valve is a hydraulic valve which is actuated electrically in a known manner. The electrical signals are generated in a known manner from the crank mechanism, the pulse generator or other power-dependent measuring points. A cam control is also suitable for controlling the hydraulic valve.
  • a check valve is arranged in the bore connected to the fuel discharge line, and this check valve closes off the bore leading to the interrupter valve and has a free passage in the direction of the bore.
  • the slide body of the main slide is connected to a push rod, at least part of the push rod forms the core of a magnetic coil, and this magnetic coil is connected to an electrical pulse generator and / or the push rod is part of a mechanical locking device and this locking device fixes the push rod and the slide body of the main slide in a control position.
  • a preferred embodiment of the invention is characterized in that the control device in the hydraulic system is connected to a camshaft control and the cam disk acts on the push rod of the control device.
  • a camshaft of low mass can be used, since it only has to move control elements. This is in contrast to injection devices, in which the camshaft drives the pump pistons directly, and which require a heavy and complex construction.
  • the control camshaft acts directly on the push rod of the main slide and serves as a 3-actuator gan of the main slide or as an emergency control in case of failure of the solenoid.
  • the axial piston is double-acting and the pressure medium supply line to the working space with the fully loaded piston surface is led directly to the pressure source via the control device to the pressure source and the pressure medium supply line to the annular space with the annular surface of the piston.
  • the pump piston When the fuel injection device according to the invention is operated, the pump piston is rotated about its longitudinal axis depending on the engine output by means of a control device known per se and brought into a position in which the control edges effect the injection of the desired amount of fuel.
  • the start of the injection process is effected via the first control device in the pressure medium system by means of an electrical pulse via the magnetic coil or by means of the control camshaft.
  • the first control device releases the pressure medium inflow: to the axial piston unit and this moves the pump piston, the fuel in the pump chamber being pressurized.
  • the control valve to the injection nozzle opens and the fuel is injected into the diesel engine under pressure up to 2000 bar.
  • the pump space is coupled to the two control devices via the first relief bore and the connecting lines, and the sudden one moves at the speed of sound Spreading pressure surge causes a resetting of the auxiliary slide via the return pistons in the first control device and thereby blocks the main flow of pressure medium to the fully loaded piston surface of the axial piston unit.
  • the axial and pump pistons are only fed by means of the reduced pressure medium flow through the throttle bore of the auxiliary slide.
  • the pressure surge acts on the switching piston unit of the second control device and opens the overflow / suction valve.
  • the pressure in the pump chamber relaxes through the feed line into the fuel discharge line, and the injection process is interrupted.
  • the pre-injection phase can be adjusted in a known manner by rotating the piston about the longitudinal axis.
  • the pump piston is ready to continue the injection and moves at a reduced speed.
  • the closed interrupter valve is opened, thereby relieving the pressure on the piston chamber of the switching piston unit. The consequence of this is that the reset piston on the auxiliary slide of the first control unit is also relieved and the spring-loaded slide is pushed back into its first switching position.
  • the full volume flow of pressure medium hits the axial piston again, and the movement of the pump piston continues at full speed.
  • the overflow / suction valve closes immediately and pressure is built up again in the pump room.
  • the control valve opens the supply line to the injection nozzle and the main injection phase begins. During this phase, the interrupter valve in the second control device is closed again.
  • the overflow / suction valve is opened again in the manner described and the main injection phase is terminated.
  • the third annular space on the pump piston is arranged parallel to the second, and the upper control edges of the two annular spaces are at the same distance from one another as the first and the second relief bore, so the pressure surge occurs simultaneously via the connecting lines on the two return pistons of the auxiliary and of the main slide on the first control device and on the switching piston unit of the second control device.
  • the main slide opens the return in Pressure medium system, which means that when the overflow / suction valve in the fuel system is opened, the axial piston also stops and returns immediately. This ensures the immediate closure of the injection line and prevents pumping.
  • the pump piston and the axial piston are pushed into their initial positions at bottom dead center.
  • the control edge lies on the upper end face of the piston under the first relief bore.
  • the entire fuel system, including the return pistons, is thus under the same pressure.
  • the auxiliary slide also moves into its initial position and the control devices are ready for the next work cycle.
  • the stroke of the pump piston is not limited by mechanical elements.
  • the piston can therefore have a smaller diameter and a larger stroke than the known devices.
  • this fuel injection device is extremely precise.
  • the start of the injection process can be precisely determined by known and tested means and transmitted to the first control device.
  • the use of special hydraulic oils or other pressure media is possible, which ensure the long service life desired in fuel injection devices.
  • the connection of the inclined edge control on the pump piston with a pressure unit acted upon by pressure medium results in a very high level of operational safety and design independence.
  • a major advantage of this fuel injection device also consists in the fact that all components can be arranged axially with respect to one another, and when several injection devices are arranged, each is independent of the other.
  • the heavy and complex drive camshafts are eliminated completely, which is particularly important in the case of large and fast-running diesel engines. Nevertheless, the emergency control via camshaft controls with a light camshaft is guaranteed.
  • FIG. 1 shows the fuel injection device according to the invention in schematic representation with components partially shown in section.
  • FIG. 2 shows a longitudinal section through the first control device with mechanical locking device and the camshaft control.
  • FIG. 3 shows a longitudinal section through the second control device with two interrupter valves, an auxiliary valve and an additional control valve connected between the two control devices.
  • the fuel injection device shown in FIG. 1 has a fuel pump 3, an axial piston unit 28, a first control device 38, a second control device 50 and an injection nozzle 1.
  • the fuel pump 3 comprises a pump cylinder 4, a pump chamber 6, a pump piston 7 and a fuel line which consists of the fuel feed line 14, the check valve 16, the fuel channel 5, the flow line 66, the feed line 13 and the fuel discharge line 15.
  • a pressure line 2 is arranged, which contains a control valve 17 and leads to the injection nozzle 1.
  • the feed line 13 is inserted into the pump chamber 6 at the upper end thereof.
  • the pump piston 7 has a plurality of annular spaces 18, 19, 20 on its jacket, which are connected to the pump space 6 via a channel 10.
  • the first annular space 18 has control edges 22, 23, the second annular space 19 has control edges 24, 25 and the third annular 20 clean up the control edge 26.
  • the upper end surface 9 of the pump piston 7 forms a first control edge 21.
  • a first relief bore 11 and a second relief bore 12 are arranged in the pump cylinder 4. When the pump piston 7 is at bottom dead center, the first relief bore 11 opens into the pump chamber 6 above the upper end face 9 of the pump piston 7.
  • the second relief bore 12 is arranged at a distance from the first relief bore 11 which corresponds to the maximum stroke corresponds to the pump piston 7.
  • the pump piston 7 can also be rotated about its longitudinal axis 8, for which purpose a known adjusting device 125 is provided. Furthermore, the pump piston 7 is connected at its lower end to the axial piston unit 28 of a drive unit 27.
  • the axial piston unit 28 consists of a cylinder 29 and a double-acting axial piston 30 and is connected via pressure medium lines 35, 36 to a pressure source 37 also belonging to the drive unit 27.
  • the double-acting axial piston 30 has a piston surface 31 directed towards the working space 33, which is opposite an annular surface 32 assigned to the annular space 34.
  • the drive unit 27 is operated with any known pressure medium and forms a pressure medium system. In the present example, high-pressure hydraulic oil is used.
  • the first control device 38 which has a pressure line 42, a return line 43 and a leak line 44, is also located in the pressure medium system.
  • the pressure medium line 35 which opens into the working space 33 of the axial piston unit 28, is also connected to the first control device 38.
  • connecting lines 45, 46 are connected to the first control device 38, which lead to the relief bores 11 and 12 on the pump cylinder 4.
  • the connecting lines 45, 46 are connected to one another via a further connecting line 47, in which a check valve 48 is installed.
  • This check valve 48 prevents fuel from the line 46 flows to line 45 or to the main slide.
  • An electrical pulse generator 39 is arranged next to the first control device 38 and connected to it. This pulse generator 39 is connected in a known manner to the 5 remaining measuring and control elements of the internal combustion engine and controls the injection processes according to requirements.
  • a pressure control valve 40 and a pressure medium and outlet 10 in a known manner . equal container 41 arranged.
  • the connecting line 46, the flow line 66 and the feed line 13 are connected to the second control device 50.
  • This has a through bore 64
  • An overflow / suction valve 51 is installed in this bore, which has a valve seat 61, a valve stem 58 and a switching piston 52.
  • valve seat 61 can fuel from the fuel feed line
  • a fuel pump (not shown) is arranged in the fuel feed line 14 to support the fuel flow.
  • the overflow / suction valve 51 is loaded with a spring 59 which closes the valve seat 61.
  • the switching piston 52 which rests on the valve stem 58, is located below
  • a piston chamber 57 is formed, which is connected via a line 49 to the connecting line 46 and the relief bore 11.
  • a spring 60 is arranged in the piston chamber 57, which presses the switching piston 52 against the valve stem 58 and
  • the piston chamber is located above the bores 63, 65 and an interrupter valve 53 57 also in connection with the bore 64 or the fuel discharge line 15. Between the bores 63 and 65, a compensating valve 54 is connected, which facilitates the afterflow of fuel into the various bores.
  • a check valve 55 arranged opposite the interrupter valve 53 prevents pressure surges in the bore 64 from opening the closed interrupter valve 53. Such pressure surges can occur when the overflow / suction valve 51 is opened at high pressure in the pump chamber 6 and the pump pressure flows through the feed line 13 into the bore 64 and the fuel discharge line 15. Depending on the pressure in the pump chamber 6, such pressure surges can reach up to 200 bar in the short term.
  • the interruption valve 53 is actuated by a control 56, which is a known electrical control or a mechanical control, which is connected to the camshaft control acting on the first control device 38.
  • the first control device 38 is shown in section in FIG. 2 and essentially consists of a main slide 70, an auxiliary slide 71, a mechanical locking device 69 and a camshaft control 110.
  • the main slide 70 has two slide bodies 77, 78 with control edges and locking seats 82, 83 on.
  • An annular space 79 is assigned to the slide body 77 and an annular space 81 is assigned to the slide body 78.
  • Pressure relief spaces and sealing pistons are arranged behind each of the slide bodies 77 and 78, the pressure relief spaces being connected to a leakage line 44.
  • the slide bodies 77, 78 and the sealing pistons are arranged at the correct distance from one another by means of a core and connected to one another.
  • the annular space 81 is connected to the return line 43, the annular space 79 to the pressure lines 42 and 36, and the annular space 80 via a connecting line 89 to an annular space 86 of the auxiliary slide 71.
  • a push rod 96 is arranged at one end of the main slide 70 which with the slider bodies 77, 78 is connected, part of the push rod 96 forming the core 98 of a solenoid 97.
  • the push rod 96 extends beyond the magnetic coil 97 and is enclosed by the mechanical locking device 69.
  • the camshaft control 110 is connected to this mechanical locking device 69.
  • a return piston 72 acts together with the slide bodies 77, 78 via a pin 76.
  • a ge to return piston 72 listening piston chamber 73 is "via the connecting line 45 with the fuel system in combination.
  • These tants ⁇ line 45 as stungsbohrung seen from Figure 1 in the Entla ⁇ 12 is inserted in the pump cylinder 4, which leads to the pump space 6 Via the connecting line 47 and the check valve 48, the piston chamber 73 is also connected to the connecting line 46 and thus to the relief bore 11 in the pump cylinder 4, or the piston chamber 57 in the second control device 50.
  • the auxiliary slide 71 has a slide body 84 and two annular spaces 85, 86. Pressure relief spaces and sealing pistons are likewise arranged behind the slide body 84 and the annular spaces 85, 86, the pressure relief spaces being connected to the leak line 44. Between the two
  • Annular spaces 85, .86 is the locking seat 87.
  • the annular space 86 is connected to the pressure line 42 or the return line 43 via the connecting line 89.
  • the pressure medium line 35 extends from the annular space 85 and leads to the working space 33 of the axial piston unit 28.
  • a throttle bore 88 is located in the slide body 84, which allows a reduced flow of hydraulic oil from the annular space 86 into the annular space 85 and vice versa even when the locking seat 87 is closed.
  • the auxiliary slide 71 also interacts with a return piston 74 at one end.
  • a piston chamber 75 belonging to the resetting piston 74 stands over the connecting Connection line 46 with the fuel system or with the relief bore 11 on the pump cylinder 4 and the piston chamber 57 in connection with the second control device 50.
  • the auxiliary slide 71 is loaded with a spring 94 which is arranged in the leakage space 95 and pushes the auxiliary slide 71 back into the starting position.
  • FIG. 2 shows the mechanical locking device 69 and the camshaft control 110.
  • the mechanical locking device 69 essentially consists of a locking body 100, tabs 104 and unlocking bolts 106.
  • the push rod 96 projects into the locking body 100 and has a shoulder 101 in its area. If the push rod 96 is moved to the left by means of the solenoid coil 97, the shoulder 101 takes the locking body 100 with it, and the spring-loaded pawls 104 snap into the cams 105 and hold the locking body 100 in position. As a result, the power supply to the solenoid coil 97 can be interrupted and there is no risk of overloading or overheating.
  • the push rod 96 is reset at the end of the injection process via the return piston 72, which is acted upon by the injection pressure.
  • the push rod 96 is pressed to the right against the force of the spring 102 and the unlocking bolts 106 are driven outwards from the end of the push rod 96.
  • These unlocking bolts 106 raise the pawls 104 and thereby release the cams 105 on the locking body 100.
  • the spring 103 now pushes the locking body 100 back into its starting position.
  • the camshaft control 110 is arranged in addition to the solenoid 97 of the injection control. This consists of the cam disk 107 with a cam 108 and the
  • Control body 100 attached roller 109.
  • the camshaft is driven by a drive, not shown, which communicates with the crank mechanism.
  • the cam 108 drives the blocking body 10 O0 and thus the push rod 96 to the left at the start of the injection process via the idler roller 109.
  • the movement of the control body 100 and the push rod 96 requires only small forces, and the camshaft control 110 can therefore be built easily and without great kinematic effort.
  • the push rod 96 is reset at the end of the injection process in the same way as described above.
  • a second magnetic coil 99 is arranged in addition to the magnetic coil 97.
  • Both solenoids 97, 99 receive electrical impulses from the electrical pulse generator 39 via the electrical line 93.
  • the solenoid 99 By actuating the solenoid 99 with an electrical pulse, the push rod 96 can be shifted to the right and the injection process can therefore be stopped prematurely. This enables an emergency stop of the injection device, since this action of the main slide 70 interrupts the action on the axial piston 30 of the axial piston unit 28 and pushes the axial piston 30 back.
  • the second control device 50 shown in FIG. 3 is an embodiment which allows higher switching speeds and fulfills emergency operation functions.
  • This improved control device has, in the same way as that shown in FIG. 1, an overflow / suction valve 51 with a switching piston 52, a compensating valve 54 and a check valve 55
  • Flow line 66 fuel flows into the overflow conduit 62 and from there either via the overflow / suction valve 51 and the feed line 13 into the pump chamber 6 or via the bore 64 to the fuel discharge line 15.
  • the check valve 55 has a free passage 68 through which the fuel can flow from the bore 64 into the line 15.
  • the check valve 55 is open, the Valve chamber 114 in connection with the fuel line 15 via the bore 67.
  • the piston chamber 57 of the switching piston 52 is connected via the line 49 and the lines 45 and 46 to the relief bores 11 and 12 in the pump cylinder 4.
  • a second interrupter valve 111 is installed in the bores 63, 65 between the piston chamber 57 and the fuel discharge line 15.
  • a further auxiliary valve 117 is arranged next to the interrupter valve 53.
  • the interrupter valve 111 has a control piston 113 and a piston chamber 118, the piston chamber 118 being connected via the line 119 to the line 45 or the relief bore 12. If there is no pressure in the piston chamber 118, the interrupter valve 111 is pressed against the lower stop by a spring 120 and is open.
  • the interrupter valve 53 has a control piston 112 and a piston chamber 115 which is connected to the valve chamber 114 via the line 116. The interrupter valve 53 is pressed against the valve seat by a spring 126 when there is no pressure in the piston chamber 115 and keeps this valve closed.
  • the auxiliary valve 117 which has a piston 121, a piston chamber 123 and a spring 122, is arranged in the line 116 between the piston chamber 115 and the valve chamber 114.
  • the spring 122 presses the piston 121 against the stop, and the auxiliary valve 117 is open.
  • the piston chamber 123 is connected via the line 124 to a switching valve 90, which in turn is connected to the auxiliary slide 71 of the control device 38 via the control lines 91, 92.
  • the control line 91 opens into the annular space 86 and the control line 92 into the leakage space 95 connected to the leakage line at the auxiliary slide 71.
  • the switching valve 90 is a three-way valve which is provided by the pulse generator 39 electrically or by a camshaft is operated.
  • the operation of the fuel injection device shown in FIG. 1 takes place in such a way that fuel flows from the fuel feed line 14 via the fuel channel 5, the line 66, the open suction valve 51 and the feed line 13 into the pump chamber 6.
  • the pump piston 7 is in its lowest position and the axial piston 30 connected to the pump piston 7 is also at the bottom dead center.
  • the main slide 70 of the first control unit 38 is held in its initial position by the spring 103, and the slide body 77 closes the connection of the pressure line 42 to the pressure medium line 35.
  • the magnetic coil 97 is excited by the electrical pulse generator 39 and via the push rod 96 the main slide 70 is displaced in the direction of the return piston 72.
  • the slide body 77 releases the connection " between the annular space 79 and the annular space 80.
  • the slide body 78 closes the connection between the annular space 80 and the annular space 81.
  • Pressure medium thus flows in under pressure from the pressure line 42 via line 89 the annular spaces 86, 85 on the auxiliary slide 71 and in the line 35 and thus in the working space 39 of the axial piston unit 28.
  • the axial piston 30 moves upward and pushes the pump piston 7 in the direction of the upper end of the pump chamber 6.
  • This axial movement makes the relief bore 11 in the pump cylinder 4 is closed, and pressure is built up in the pump chamber 6.
  • the control valve 17 opens and fuel is injected into the combustion chamber of a diesel engine via the injection nozzle 1.
  • the pressure prevailing in the pump chamber 6 is increased by a pressure channel 10 attached to the jacket of the pump piston 7, the annular spaces 18, 19 and 20 fed.
  • the pressure built up in the pump space 6 propagates as a pressure surge via the lines 46 and 49 into the first and second control devices 38 and 50.
  • the first control device 38 as can be seen from FIG Return piston 74 is acted upon by the pressure surge via the piston chamber 75.
  • the auxiliary slide 71 is displaced against the force of the spring 94, and the slide body 84 closes the locking seat 87.
  • the switching piston 52 is acted upon by the pressure surge in the second control device 50 via the piston chamber 57. The switching piston 52 moves upward and opens the overflow / suction valve 51 or its valve seat 61 via the valve shaft 58.
  • the pressure prevailing in the pump chamber 6 thus immediately relaxes in the overflow chamber 62, the bore 64 and in the fuel discharge line 15.
  • the sudden drop in pressure causes the control valve 17 to close immediately and the injection process is interrupted.
  • the relief bore 11 is after a short movement of the piston 7 through the lower control edge 23 of the annular space 18 again. closed, and the overflow / suction valve 51 is held in the open position by the fuel volume present in the piston chamber 57.
  • the pressure in space 57 is higher than in space 62.
  • the springs 59, 60 support the movements of the valve 51. Since the annular space 18 is only the
  • the distance between the control edges 22, 23 can be chosen to be very small.
  • the interrupter valve 53 is opened quickly by the control 56 being actuated.
  • the bore 65 is connected to the fuel discharge line 15 and the auxiliary slide 71 in the first control device 38 can be pushed back into its starting position by the spring 94.
  • the overflow / suction valve 51 is closed by the same pressure relief.
  • the control valve 17 opens again and the main phase of the injection begins.
  • the interrupter valve 53 is closed again with the aid of the control 56.
  • the main injection phase continues until the control edges 24 and 26 of the two annular spaces 19 and 20 reach the relief bores 11 and 12.
  • the two control antennas 24 and 26 are arranged at the same distance from one another as the two relief bores 11 and 12.
  • the pressure prevailing in the pump chamber 6 becomes in the form of a pressure surge via lines 45, 46 and 49 transmit the two control devices 38 and 50.
  • the return piston 72 is acted upon by the pressure surge in the line 45 and via the piston chamber 73 and the main slide 70 is pushed back.
  • the slide body 77 interrupts the connection between the annular spaces 79 and 80, and the slide body 78 opens the connection between the annular spaces 80 and 81, with which the working space 33 on the axial piston unit 28 is connected to the return line 43. Since the auxiliary slide 71 was also displaced by the pressure surge on the return piston 74, the locking seat 87 is closed by the slide body 84. The pressure medium can therefore only flow back from the working space 33 via the line 35 and the throttle bore 88 at a limited speed, thereby preventing the piston from shooting back. At the same time, as already described above, the overflow / suction valve 51 opens the valve seat 61 on the second control device 50, and the pressure in the pump chamber 6 is immediately reduced.
  • the control valve 17 closes and the main injection process is ended.
  • the entire fuel system and thus also the annular spaces 18, 19 and 20 on the pump piston 7 and the lines 45, 46, 49 are thus again under the normal pressure of the fuel feed pump and the auxiliary slide 71 is pushed back into the starting position by means of the spring 94 .
  • the slider body 84 opens the Lock seat 87 and releases the full backflow cross section.
  • the pressure of the pressure medium system prevailing in the annular space 34 of the axial piston unit 28 pushes the axial piston 30 back until it has reached its starting position again at bottom dead center. The device is thus ready for a further injection process.
  • two interrupter valves 53 and 111 are used in the second control device 50, these valves are also switched with the aid of the pressure surges branched off from the pump chamber 6 via the relief bores 11 and 12.
  • the use of two Unter ⁇ breaker valves 53, 111 having respective control pistons 112, 113 ensures the operation up to the maximum lift in case of failure of the controller 56 according to FIG 1 or the 'on-off valve 90 or the control thereof.
  • the auxiliary valve 117 is open in the unpressurized state in the piston chamber 123 by the spring force 122.
  • the pressure from the pump chamber 6 acts as a pressure surge from the relief bore 11 via the line 49 and the connecting line 116 to the control piston 112, and the interrupter valve 53 opens.
  • the overflow / suction valve 51 closes immediately and the injection is continued.
  • the valve 53 also closes again.
  • the piston 7 continues to move upward, the injection phase being continued.
  • the pressure from the pump chamber 6 acts as a pressure surge via lines 49 and 119.
  • the pressure surge via line 49 acts on the switching piston 52 and opens the overflow / suction valve - til 51.
  • the second interrupter valve 111 is simultaneously closed by the pressure surge from the pump chamber 6 via the relief bore 12, the connecting line 119 and the action on the control piston 113, so that the overflow / suction valve remains open and the injection is ended.
  • the pressure in the entire fuel system and also in the piston chamber 118 drops, so that the valve 111 is pushed back by the spring 120 and is open again for the next delivery stroke stands.
  • a spindle 127 on the interrupter valve 111 With the aid of a spindle 127 on the interrupter valve 111, overlapping control movements can be carried out during the injection stroke.
  • Actuating the spindle 127 which is known per se and not shown, for example in connection with the switching valve 90, results in shorter switching intervals for the overflow / sucking valve 51.
  • the second interrupter valve 111 can already be closed during the opening process of the first interrupter valve 53 and vice versa.
  • the open interrupter valve 111 is kept open by closing the auxiliary valve 117.
  • the switching valve 90 ensures that the auxiliary valve 117 is opened at the correct time and thus the interrupter valve 53 is closed.
  • the switching valve 90 for the auxiliary valve 117 is controlled in a known manner as a function of power and speed, as is the control of the adjustment device 125 on the pump piston 7.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Une pompe à injection (3) est entraînée par un système d'entraînement (27) à piston axial (28). Le système d'entraînement (27) est relié à une première unité de commande (38) munie de tiroirs pricipal et secondaire. Le milieu de pression du système d'entraînement (27) n'est pas en contact physique avec le circuit de carburant. Des pistons de commande sur la première unité de commande sont reliés avec des perçages de décharge (11, 12) du cylindre (4) de la pompe (3) ainsi qu'avec une seconde unité de commande (50). Des espaces annulaires (18, 19, 20) s'ouvrant dans la chambre de pompage (6) sont ménagés sur le corps de piston (7) de la pompe (3). Les espaces annulaires (18, 19, 20) coopèrent avec les perçages de décharge (11, 12) et sont pourvus d'arêtes de commande. Au moins l'un (18) de ces espaces annulaires provoque un arrêt de l'injection de carburant par l'injecteur (1). Plusieurs soupapes (51, 53) de la seconde unité de commande (50) régulent la pression dans la chambre (6) de la pompe et commandent l'admission et le refoulement du carburant. Des à-coups de pression se produisant au niveau des perçages de décharge (11, 12) provoquent des mouvements d'actionnement dans les deux unités de commande (38, 50).
EP87905421A 1986-09-09 1987-09-04 Dispositif d'injection de carburant dans un moteur diesel avec preinjection Expired - Lifetime EP0282508B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87905421T ATE61449T1 (de) 1986-09-09 1987-09-04 Brennstoffeinspritzvorrichtung fuer eine dieselbrennkraftmaschine mit voreinspritzung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3617/86A CH671073A5 (fr) 1986-09-09 1986-09-09
CH3617/86 1986-09-09

Publications (2)

Publication Number Publication Date
EP0282508A1 true EP0282508A1 (fr) 1988-09-21
EP0282508B1 EP0282508B1 (fr) 1991-03-06

Family

ID=4259828

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87905421A Expired - Lifetime EP0282508B1 (fr) 1986-09-09 1987-09-04 Dispositif d'injection de carburant dans un moteur diesel avec preinjection

Country Status (11)

Country Link
US (1) US4878471A (fr)
EP (1) EP0282508B1 (fr)
JP (1) JPH0681934B2 (fr)
KR (1) KR940011343B1 (fr)
CN (1) CN1010335B (fr)
AT (1) ATE61449T1 (fr)
CH (1) CH671073A5 (fr)
DE (1) DE3768490D1 (fr)
FI (1) FI882145A (fr)
PL (1) PL157237B1 (fr)
WO (1) WO1988002066A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5392749A (en) * 1991-10-11 1995-02-28 Caterpillar Inc. Hydraulically-actuated fuel injector system having separate internal actuating fluid and fuel passages
US5492098A (en) * 1993-03-01 1996-02-20 Caterpillar Inc. Flexible injection rate shaping device for a hydraulically-actuated fuel injection system
JP2885076B2 (ja) * 1994-07-08 1999-04-19 三菱自動車工業株式会社 蓄圧式燃料噴射装置
US5730104A (en) * 1997-02-19 1998-03-24 Caterpillar Inc. Injection rate shaping device for a fill metered hydraulically-actuated fuel injection system
DE19716221B4 (de) * 1997-04-18 2007-06-21 Robert Bosch Gmbh Kraftstoffeinspritzeinrichtung mit Vor- und Haupteinspritzung bei Brennkraftmaschinen, insbesondere für schwer zündbare Kraftstoffe
CA2370850A1 (fr) * 1999-05-18 2000-11-23 Ning Lei Dispositif de commande hydraulique a deux etages et a double effet
DE10126686A1 (de) * 2001-06-01 2002-12-19 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung mit Druckverstärker
SE523498C2 (sv) * 2001-08-17 2004-04-27 Volvo Teknisk Utveckling Ab Förfarande för att styra bränsleinsprutningen till ett förbränningsrum samt en bränsleinsprutningsanordning för att genomföra förfarandet
JP3993841B2 (ja) * 2003-06-12 2007-10-17 ヤンマー株式会社 低温始動進角機構を備える燃料噴射ポンプ
KR101219877B1 (ko) * 2011-05-13 2013-01-09 현대중공업 주식회사 디젤엔진용 하이브리드 연료분사 장치
DK179219B1 (en) * 2016-05-26 2018-02-12 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland Fuel or lubrication pump for a large two-stroke compression-ignited internal combustion engine

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB514011A (en) * 1938-04-26 1939-10-27 Gardner & Sons Ltd Improvements relating to fuel injection pumps for compression ignition oil engines
CH352531A (fr) * 1958-04-12 1961-02-28 Etienne Bessiere Pierre Pompe d'injection
CH589557A5 (fr) * 1974-12-24 1977-07-15 Rieter Ag Maschf
GB1592350A (en) * 1976-11-09 1981-07-08 Lucas Industries Ltd Fuel systems for an internal combustion engine
US4275087A (en) * 1979-05-15 1981-06-23 International Flavors & Fragrances Inc. Flavoring with 2,6,6-trimethyl-α-propenyl-1,3-cyclohexadiene-1-methanol substances
FR2482669A2 (fr) * 1979-05-28 1981-11-20 Semt Perfectionnement a une pompe d'injection pour un moteur a combustion interne
DE3001155A1 (de) * 1980-01-15 1981-07-16 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzanlage fuer selbstzuendende brennkraftmaschine
DE3100725A1 (de) * 1980-12-16 1982-07-01 Gebrüder Sulzer AG, 8401 Winterthur "einrichtung zur gesteuerten foerderung des brennstoffs in einer brennkraftmaschine"
US4417557A (en) * 1981-07-31 1983-11-29 The Bendix Corporation Feed and drain line damping in a fuel delivery system
US4499876A (en) * 1981-10-30 1985-02-19 Nippondenso Co., Ltd. Fuel injection control for internal combustion engines
US4425893A (en) * 1981-12-07 1984-01-17 The Garrett Corporation Fuel injection
US4667638A (en) * 1984-04-17 1987-05-26 Nippon Soken, Inc. Fuel injection apparatus for internal combustion engine
JPS61261653A (ja) * 1985-05-16 1986-11-19 Nippon Soken Inc 燃料供給装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO8802066A1 *

Also Published As

Publication number Publication date
WO1988002066A1 (fr) 1988-03-24
CN1010335B (zh) 1990-11-07
JPH01500844A (ja) 1989-03-23
FI882145A0 (fi) 1988-05-06
US4878471A (en) 1989-11-07
KR940011343B1 (ko) 1994-12-05
KR880701825A (ko) 1988-11-05
CN87106778A (zh) 1988-06-08
PL267641A1 (en) 1988-08-04
JPH0681934B2 (ja) 1994-10-19
CH671073A5 (fr) 1989-07-31
DE3768490D1 (de) 1991-04-11
PL157237B1 (en) 1992-05-29
EP0282508B1 (fr) 1991-03-06
FI882145A (fi) 1988-05-06
ATE61449T1 (de) 1991-03-15

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