EP0629265A1

EP0629265A1 - Fuel injecting device working according to the solid energy accumulator principle, for internal combustion engines.

Info

Publication number: EP0629265A1
Application number: EP93905299A
Authority: EP
Inventors: Wolfgang Dr Heimberg; Wolfram Hellmich; Pau Malatinszky; Franz Koegl
Original assignee: Ficht GmbH
Current assignee: Ficht GmbH and Co KG
Priority date: 1992-03-04
Filing date: 1993-03-04
Publication date: 1994-12-21
Anticipated expiration: 2013-03-04
Also published as: JPH09177636A; EP0725215B1; CA2127799A1; US6188561B1; ATE154100T1; CA2127801A1; US5520154A; EP0629264A1; AU681827B2; AU667345B2; JPH07504475A; EP0725215A3; DE59308851D1; EP0630442B1; JPH07504476A; JP2867334B2; HK1013676A1; DE59306679D1; EP0629264B1; EP0733798A3

Abstract

The fuel injection system has a unit for producing increase in pressure which includes an impingement device (25), e.g. a rear wall or a piston type stop. The impingement device is provided in a fuel storage element (6) arranged outside an injection pump (1), connected at a pressure line (2) between the injection pump and the injection nozzle (3). The storage element (6) includes a fuel storage chamber (22), in which a spring preloaded diaphragm (23) is arranged. One side of the chamber is arranged at a specified distance to the diaphragm.

Description

, _

FUEL INJECTION DEVICE USING THE SOLID ENERGY STORAGE PRINCIPLE FOR INTERNAL COMBUSTION ENGINES

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 that delivery pressure builds up is required to spray the fuel through the injector. 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.

In a so-called pump nozzle element known from DD-PS 120 514, which works on the solid-state energy storage principle, the fuel delivery chamber accommodating the delivery piston of the injection pump has axially parallel grooves in a first section the inner wall through which fuel can flow to the rear of the delivery piston when the delivery piston starts to move without any noticeable pressure build-up in the fuel. The adjoining second section of the fuel delivery space is the actual pressure space, which has no grooves. If the accelerated delivery piston enters this pressure chamber, it is suddenly braked by the incompressible fuel, as a result of which 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).

According to DD-PS 213 472, 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 surface can be kept reasonably small. The disadvantage here, however, is that the impacting process leads to a high level of wear on the bodies that meet. In addition, 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 be adapted to the load conditions of the engine only to a very limited extent. The same applies to the fuel injection device according to DE OS 23 07 435, in which the reciprocating piston pump has a sleeve-shaped pump cylinder as the movable pump member, which

* is slidably arranged on a pump piston which is firmly seated in the pump housing and delimits the pump pressure space, which via _r . a longitudinal bore in the pump piston is connected to the injection valve device. A cross hole in the pump cylinder allows fuel to flow to the back of the cylinder when storing energy. Driving over the piston end edge 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 fuel can be injected without any noticeable pressure losses during pressure build-up and can be precisely controlled depending on the load, and which in particular for high-speed internal combustion engines suitable is.

This object is achieved by the characterizing features of claim 1. Advantageous further developments of the invention are characterized in the subclaims.

The invention is explained in more detail by way of example with reference to the drawing. Show it:

1 to 19 schematically in longitudinal section different embodiments of the injection device according to the invention,

_* Fig. 20, 21 and 22 schematically shows a spraying device according to the invention the Ein¬ groundwork for forming fuel supply _ an engine start and an engine emergency operation without a battery,

23 schematically shows a preferred circuit for controlling the coil of the injection device according to the invention, 24, 25 and 26 preferred embodiments of the injection valve of the injection device according to the invention in longitudinal section, and

27 shows a fuel supply device without return line to the tank.

In the invention, an initial partial stroke of the delivery element of the injection pump is provided, in which the displacement of the fuel does not result in a pressure build-up, the delivery element partial stroke serving for energy storage expediently being carried out by a storage volume, e.g. is determined in the form of an empty volume and a stop element which, as will be explained in more detail below with reference to the exemplary embodiments, can be designed differently, for example in the form of a spring-loaded membrane or a spring-loaded piston element against which fuel is delivered and which allow the displacement of fuel on a stroke path "X" of the delivery element; only when the spring-loaded element is pressed against a e.g. abuts a firm stop, an abrupt pressure build-up is generated in the fuel so that the fuel is displaced in the direction of the injection nozzle.

1 has an electromagnetically driven reciprocating piston pump 1, which is connected via a delivery line 2 to an injection nozzle device 3. A suction line 4 branches off from the delivery line 2 and is connected to a fuel reservoir 5 (tank). In addition, a volume storage element 6 is connected to the delivery line 2, for example in the area of the connection of the intake line 4, via a line 7.

The pump 1 is designed as a piston pump and has a housing 8 in which a magnet coil 9 is mounted, an armature 10 which is arranged in the region of the coil passage and is designed as a cylindrical body, for example as a solid body, and is guided in a housing bore 11. in the area of central is located along the longitudinal axis of the toroidal coil 9, and is pressed by means of a pressure spring 12 into an initial position in which it rests on the bottom 11a of the housing bore 11. The compression spring 12 is supported on the end face of the armature 10 on the injection nozzle side and on an annular step 13 of the housing bore 11 opposite this end face. The spring 12 comprises, with Sr. 1, a delivery piston 14 which is connected to the armature 10 on the end of the spring 12 acted upon anchor end face is firmly, for example in one piece, connected. The delivery piston 14 plunges relatively deep into a cylindrical fuel delivery chamber 15, which is formed coaxially in the axial extension of the housing bore 11 in the pump housing 8 and is in transmission connection with the pressure line 2. Because of the depth of immersion Druckyerluste can be avoided during the sudden pressure increase, the manufacturing tolerances between ^"~ ^ Lben 14 and cylinder 15 may even be relatively cross-country race only in the I, for example - need iridertstel millimeters to lie terbereiuh so that the production cost is low .

A check valve 16 is arranged in the intake line 4. In the housing 17 of the valve 16, a ball 18 is arranged as a valve element, for example, which in its rest position is pressed by a spring 19 against its valve seat 20 at the end of the valve housing 17 on the reservoir side. For this purpose, the spring 19 is supported on the one hand on the ball 18 and on the other hand on the wall of the housing 17 opposite the valve seat 20 in the region of the mouth 21 of the suction line 4.

The storage element 6 has, for example, a two-part housing 22, in the cavity of which a membrane 23 is tensioned as the organ to be displaced, which separates a space filled with fuel from the pressure line and which, in the relaxed state, the cavity in two adherences shares that are sealed against each other by the membrane. On the side of the membrane 23 facing away from the line 7, a spring force acting on it acts in an empty space, the storage volume, for example a spring 24, which acts as a return spring for the membrane 23 is set up. The spring 24 is supported with its end opposite the membrane on an inner wall of the cylindrically widened empty cavity. The empty cavity of the housing 22 is delimited by an arch-shaped wall which forms a stop surface 22a for the membrane 23.

The coil 9 of the pump 1 is connected to a control device 26, which serves as an electronic control for the injection device.

In the de-energized state of the coil 9, the armature 10 of the pump 1 is located on the base 11a due to the pretensioning of the spring 12. The fuel supply valve 16 is closed and the storage membrane 23 is held in the housing cavity by the spring 24 in its position remote from the stop surface 22a.

When the coil 9 is actuated via the control device 26, the armature 10 with the piston 14 is moved in the direction of the injection valve 3 against the force of the spring 12. The delivery piston 14 connected to the armature 10 displaces fuel from the delivery cylinder 15 into the space of the storage element 6. The spring forces of the springs 12, 24 are relatively soft, so that fuel displaced by the delivery piston 14 during the first partial stroke of the delivery piston 14 presses the storage membrane 23 into the empty space almost without resistance. As a result, the armature 10 can initially be accelerated almost without resistance until the storage volume or empty space volume of the storage element 6 is exhausted by the membrane 23 striking the arch wall 22a. The displacement of the fuel is suddenly stopped and the fuel is suddenly compressed due to the already high kinetic energy of the delivery piston 14. The kinetic energy of the armature 10 with the delivery piston 14 acts on the liquid. This creates a pressure surge that travels through the pressure line 2 to the nozzle 3 and there leads to the spraying of fuel. For the end of the delivery, the coil 9 is switched off. The armature 10 is moved back to the floor 11a by the spring 12. The amount of liquid stored in the storage device 6 is sucked back into the delivery cylinder 15 via the lines 7 and 2 and the membrane 23 is pushed back into its starting position due to the action of the spring 24. At the same time, the fuel supply valve 16 opens, so that fuel is sucked out of the tank 5.

A valve 16a is expediently arranged in the pressure line 2 between the injection valve 3 and the branches 4, 7 and maintains a standing pressure in the space on the injection valve side, which e.g. is higher than the vapor pressure of the liquid at the maximum temperature, so that bubble formation is prevented. The parking pressure valve can e.g. be designed as the valve 16.

A storage piston 31 can also be used as a displacement element for the storage element 6 instead of the membrane 23. The stop which suddenly stops storing in this case can be designed to be adjustable according to the invention, so that the distance of the acceleration stroke of armature 10 and delivery piston 14 can be changed. A cable pull, for example coupled to the throttle valve of the engine, is preferably used for this adjustment. Alternatively, the adjustment can expediently be controlled by the control device 26, for example by means of an actuating magnet. Figure 2 shows e.g. an embodiment of the storage element 6 with a displacement piston 31 adjustable by a cable 40.

The storage element 6 according to FIG. 2 has a cylindrical housing 30 which can be formed integrally with the pressure line 2. As the organ to be displaced, a storage piston 31 is used, which is guided with a close fit on the inner wall of the cylinder housing 30, so that no significant leakage can occur, with an empty volume 33c being provided in the cylinder 30, into which the piston 31 can be displaced. Existing leakage liquid speed can escape through a drain hole 32 from the empty volume space 33c and is supplied to the fuel tank 5 (see FIG. 1). The drain hole 32 is formed in the cylinder wall of the housing 30 in the region of the housing cover 33, which lies opposite the housing wall 33a, which is integrally formed with a wall section of the pressure line 2. The drain hole 32 extends approximately radially to the central longitudinal axis 33b of the cylindrical housing 30th

A compression spring 34 is clamped between the inside of the housing cover 33 and the end face of the piston 31 opposite this wall, which presses the piston 31 into its rest position against the opposite housing end wall 33a, in which a bore 35 is formed which ^" in the middle ¬ longitudinal axis 33b of the housing 30 and opens into the pressure line 2.

The housing cover 33 of the housing 30 is extended in a tubular manner in the axial direction, and in the passage of the extension tube 36 a stop bolt 37 is slidably guided like a piston and has a ring 38 at the end located in the space 33c. The piston 31 abuts against the underside of the ring 38 when it is moved from its rest position towards the housing cover 33. This stop element 37 is preloaded by means of a spring 39. For this purpose, the spring 39 is supported on the one hand on the inside of the cover 33 and on the other hand on the ring step of the ring 38 of the bolt 37. A cable 40 is fastened to the part of the bolt 37 arranged outside the cylinder 30 and is connected, for example, to the throttle valve of the engine. The stop pin 37 can be adjusted in the direction of the central longitudinal axis 33b of the housing 30 by means of the cable 40, so that the possible stroke of the piston 31 can also be varied in accordance with the position of the stop ring 38. The stop bolt 37 can be adjusted depending on the required acceleration stroke of the armature 10 of the pump 1 (FIG. 1). The mode of operation of the memory element 6 according to FIG. 2 essentially corresponds to that of the memory element 6

In a first partial stroke of the delivery piston 14 and the armature 10 (FIG. 1), the storage piston 31 of the storage element 6 is pushed out of its rest position shown in FIG. 2 by displaced fuel, the Return spring 34 is designed to be relatively soft, so that the fuel moved by the delivery piston 14 seated on the armature 10 can be displaced almost without resistance of the storage piston 31. As a result, the armature 10 with the delivery piston 14 is almost resistance-free on part of the stroke, i.e. essentially accelerates only against the spring force of the springs 12, 34 until the storage piston 31 with its spring-loaded end face abuts the stop ring 38, as a result of which the fuel located in the delivery cylinder 15 and in the pressure line 2 abruptly due to the high kinetic energy of the armature 10 and delivery piston 14 is compressed and this kinetic energy is transferred to the liquid. The resulting pressure surge then leads to fuel being sprayed out via the nozzle 3.

The adjustable stop pin 37 is also suitable for exclusively controlling the amount of fuel to be injected for certain engines.

According to a further advantageous embodiment of the invention, it is provided that the fuel supply valve (valve 16 in FIG. 1) is designed such that it additionally acts as a storage element (corresponding to storage element 6 in FIGS. 1 and 2), so that fuel is released during the first partial stroke of the Delivery pistons almost resistance-free

»Is derived from the delivery cylinder 15 and the pressure line 2 into a storage volume, this storage element also

The distance of the first partial stroke of the delivery piston 14 determines. 3 shows a first embodiment of a fuel feed valve designed in this way, which also ensures the function of a storage element for determining the first partial stroke of the delivery piston. An advantage of this space-saving variant of the invention is that instead of two Components according to FIGS. 1 and 2, namely a fuel supply valve and a separate storage element, there is only a single component.

The valve 50 comprises an essentially cylindrical housing 51 which, in the exemplary embodiment shown, is formed in one piece with the pressure line 2. A through hole 52 is made in the housing 51, which has a section 53 on the pressure line side, which opens into the pressure line 2 via an opening 53a, and a section 53b on the suction side, which is connected to the supply line to the fuel tank 5 (FIG. 1) . Between the two coaxial holes 53 and 53b in the housing 51, a radially expanded valve space 54 is formed, which accommodates a shut-off valve element 55. The valve element 55 consists of a circular disk 56 of large diameter and a circular disk 57 of small diameter, both circular disks being formed in one piece and the circular disk 57 having a smaller diameter being arranged on the side of the bore section 53. A valve body return spring 58 presses the valve element 55 in the idle state against the pressure line end face 59 of the valve chamber 54, the spring 58 being supported on the one hand on the disk 56 of the valve element 55 and on the other on the bottom of an annular step 60 which is centrally located in the the end face 59 of the valve chamber 54 opposite end face 61 is arranged. The disk 56 can thus sealingly come to rest against the end face 61 of the valve chamber 54.

The bore section 53 of the central longitudinal bore 52 is connected to the valve chamber 54 via grooves or grooves 62 which are arranged in the housing wall 51 and which can be designed to widen in a funnel shape in the direction of the valve chamber 54 (see FIG. 3).

In the starting position shown in FIG. 3, the valve element 55 bears against the end face 59 of the valve chamber 54 due to the action of the spring 58 with the disk 57. In this position is the storage tank-side bore section 53b via the valve space 54 and the channels 62 and the bore section 53 in flow connection with the pressure line 2 and the delivery cylinder 15, the symbolically illustrated fuel tank device 5 displacing an empty space or storage volume into the fuel can be made available. If the delivery piston 14 is accelerated in the direction of the injection nozzle (arrow 3a) as a result of excitation of the coil, the displaced fuel can pass through the bore section 53, the grooves or grooves 62, the valve chamber 54 and the inlet bore 53b into the fuel reservoir almost without resistance 5 stream. The flow conditions of the valve 50 are designed such that when a certain flow velocity of the fuel is reached, the flow forces on the valve element 55 which is flushed with the fuel become greater than the biasing force of the spring 58, so that it is pressed toward the bore 53b. The valve element 55 closes with the disk 56 the inlet cross section of the bore 53b or the recess of the ring step 60, which results in an abrupt transfer of the kinetic energy of the armature 10 with the piston 14 to the fuel in the delivery cylinder 15 and in the pressure line 2, so that fuel is sprayed off via the nozzle 3 (see FIG. 1). In this version of the valve device 50, the energy storage path of the armature 10 with the piston 14 can be controlled by the excitation of the coil. The valve element 55 lifts again through the pressure of the spring 58 from the mouth of the inlet line 53b when the piston 14 or the armature 10 moves back, so that fuel can be drawn in from the tank 5.

FIG. 4 shows a variant of the component described above with reference to FIG. 3, which takes over the function of both the fuel supply and the control of the fuel injection, the partial stroke of the delivery piston serving for energy storage also being controllable via the component. An electrically controllable valve 70 is used for this purpose. At the beginning of the pressure line 2, in the immediate vicinity of the pressure or delivery chamber 15 of the pump 1, the pressure line 2 has an opening 71 to which the fuel supply line 4 is connected, into which the electrically controllable valve 70 is inserted. In a valve housing 77, the valve 70 has a spring-loaded valve plate 72, which is firmly connected to an armature 73. The armature 73 has a central axis bore 74 and at least one transverse bore 75 in the region of the valve plate 72. In the rest position, the valve 70 is opened in that the armature 73 is pressed into an end position on the pressure line side by a spring 76 pressing against the plate 72 is in which the Kraf material of the reservoir, not shown, through the bores 75 and 74 and the pressure line opening 71 with the fuel of the pressure chambers 15, 2 is in connection.

In the housing 77, a coil 78 is also arranged, which surrounds the armature 73 at a distance.

According to the invention, the injection process takes place as follows. When the pressure line 2 is completely filled, the solenoid 9 of the pump 1 is excited, as a result of which the armature delivery piston element 10, 14 of the pump 1 is accelerated out of its rest position. The fuel displaced by the piston 14 flows through the pressure line opening 71, the central bore 74, the transverse bore 75 around the valve plate 72 and into the tank-side part of the line 4 to the fuel tank. At a certain point in time, valve 70 is activated by energizing coil 78 and moving armature 73 until valve plate 72 assumes its valve seat and blocks fuel eg. The pressure line opening 71 is blocked suddenly or very quickly, so that no further fuel can escape via line 4. As a result, armatures 10 with delivery pistons 14 are braked suddenly and release the stored kinetic energy to the incompressible fuel, which results in a pressure surge through which fuel is sprayed out of the pressure line 2 via the injection valve 3, as in the case of the others Embodiments of the invention of the armature 10 with piston 14 either its full Has reached the delivery stroke or is still being moved. The injection valve 3 is hydraulically controlled in a manner known per se and is designed to be spring-loaded. The valve 70 is preferably controlled via control electronics which jointly operate the pump 1 and the shut-off valve 70.

5 shows a modification of the valve according to FIG. 3. The integral storage element inlet valve 90 has a housing 91 which is constructed in a unitary manner with the housing 8 of the pump 1 and the pressure line 2. A middle is located in the housing 91 ¬ introduced longitudinal bore 92, which ends at one end via an opening 93a in the pressure line 2 and at the other end in a cylindrical valve chamber 93, wherein channels 94 similar to the channels 62 according to FIG. 3 lead from the bore 92 to the valve chamber 93. The valve element is constructed in two parts and comprises a cylinder 95 guided in the valve chamber 93, in the cylindrical, continuous central step bore of which a piston 96 is displaceably guided. In the outer lateral surface of the cylinder 95, axially parallel grooves 97 are formed. The cylinder 95 is pressed into its rest position by a spring 98, in which it rests with its one end face on the tank-side bottom of the valve chamber 93, into which a fuel supply line 99 coming from the fuel tank opens. In the bore for receiving the piston 96 sits a spring 100 on the tank side, which presses the piston 96 against the pressure line side bottom of the valve chamber 93, so that the bore 92 is covered, a space 95a being formed for the piston 96 in the tank-side interior of the cylinder 95 becomes.

The valve 90 works as follows. When the delivery piston 14 carries out a suction stroke, fuel is sucked out of the line 99 by the cylinder 95 being lifted from the tank-side bottom surface of the valve chamber 93 by the negative pressure against the pressure of the spring 98, so that fuel is drawn along the length ¬ grooves 97, the valve chamber 93 and the grooves 94 and the bore 92 can flow into the pressure line 2. In this process lies the piston 96, as shown in FIG. 5, on the pressure line side bottom of the valve chamber 93. When the suction stroke has ended, the cylinder 95 is pressed by the spring 98 into the position shown in FIG. 5, in which the cylinder 95 rests sealingly on the tank-side bottom of the valve chamber 93.

At the beginning of the delivery stroke of the delivery piston 14, the piston 96 guided in the cylinder 95 is moved out of its abutment on the pressure line-side bottom of the valve chamber 93 due to the relatively soft design of the spring force of the spring 100 and pressed into the free space 95a, whereby in the resulting additional space in the valve chamber 93 fuel flows from the pressure chamber 15, 2, which is displaced during the conveying movement of the delivery piston 14, fuel on the tank-side end face of the piston 96 from the piston 96 via line 99 into the tank is pushed back. The delivery stroke of the delivery piston 14 is ended in that the piston 96 strikes the end of the piston 95 with its end face acted upon by the spring 100 against the step in the central longitudinal bore of the piston 95. As a result of this abrupt termination of the essentially resistance-free acceleration stroke of the armature 10 with the delivery piston 14, the formation of a very steep pressure rise in the pressure line 2 is brought about, as a result of which fuel is sprayed off via the nozzle 3 at high pressure.

According to a further variant of the invention, provision is made for the storage element 6 to be constructed in a unitary manner with the delivery piston of the reciprocating piston pump 1. A corresponding exemplary embodiment is shown in FIG. 6. A storage piston 80 serves as the storage element, which is pressed in a first central longitudinal axis step bore section 14b on the pressure line side of a step bore 14a centrally through the piston 14 and the armature 10 against a stop (not shown) on the pressure line side by a spring 81. The piston 80 projects in the rest position with its one end face into the pressure chamber 15. The bore section 14b in the delivery piston 14 receiving the storage piston 80 sits after the step 14c towards the armature 10 in a further stepped bore section 14d, on the step 14e of which the compression spring 81 is supported, which presses against the end face of the piston 80 on the anchor side. After step 14e, the bore 14a finally also passes through the armature 10 and opens into the empty armature space 11, so that air can be displaced.

The memory element of this embodiment works as follows. On a first part of the stroke of the delivery piston 14, the energy storage path, the storage piston 80 is forced into the bore of the delivery piston 14 provided for the piston, whereby an additional space for displaced fuel is available on the pressure chamber side, so that the armature 10 during the first stroke section together with the delivery piston 14 can be accelerated essentially without resistance. The resistance-free acceleration of armature 10 and delivery piston 14 is ended when the armature-side end face of the storage piston 80 comes to bear against the annular shoulder 14c of the stepped bore 14a. The consequence of this is an abrupt pressure increase, by means of which fuel is sprayed off via the nozzle 3.

The variant of the injection device according to the invention described below with reference to FIGS. 7 and 8 has a structural unit of an electrically driven reciprocating piston pump and stop means.

In the embodiment shown in FIGS. 7 and 8, a hydraulic valve and the pump and the pressure line 2 are accommodated in a common housing 121. The function and the essential structure of the pump with electromagnetic drive essentially corresponds to the previously described embodiments of the pump 1 of the device according to the invention, the fuel being sucked in via a valve 122 which is fitted into the pump housing 121 and with the pressure line 2 in connection stands (Fig. 7). In the exemplary embodiment shown, the valve 122 closes automatically due to the Bernoulli effect at a certain flow rate. The fuel flowing through the pressure line 2 during the acceleration phase passes through a gap 123 into the valve chamber 124. Between the valve cone 125 and the associated valve seat, a narrow annular gap is left, which is designed accordingly by a spring 126 acting on the valve cone 125 can be adjusted. Fuel flows through this annular gap and, according to Bernoulli, generates a lower static pressure than in the surrounding area. At a certain flow rate, the static pressure in the annular gap has dropped so far that the valve cone 125 is attracted and the valve 122 closes, as a result of which the pressure surge required to eject the fuel via the injection nozzle is generated. The pressure line 2 leading to the injection nozzle is connected to the outlet of a check valve 127, which is also structurally combined with the housing 121.

The valve cone 128 of the valve 127 is pressed against the associated valve seat by pretensioning a spring 129, the spring 129 being designed such that the valve 127 is closed when the pressure in the pressure line 2 is below the value which increases leads to an emission of fuel via the injection nozzle, which is indirectly connected to the valve 127. The check valve 127 also prevents the formation of bubbles in the pressure line 2 to the injector valve, because the check valve can ensure a standing pressure in the pressure line between the injector and the check valve which is higher than the vapor pressure of the fuel liquid.

The anchor 10 is in this embodiment with axially parallel. len slots 130 and 131 of different depths in the jacket, which are arranged distributed around the circumference of the substantially cylindrical armature. These slots prevent the formation of eddy currents when the solenoid 9 is excited and thus contribute to energy saving. With a line 120, that leads from the armature space 11 through the housing 121 to the outside, leakage oil that has penetrated into the armature space can be sucked out.

The armature of the injection pump is usually reset using the return spring provided. To achieve high spray frequencies, the armature reset time must be kept short. This can be achieved, for example, by a correspondingly large spring force of the return spring. With a reduction in the reset time, however, the impact speed of the anchor at the anchor stop increases. A disadvantage here can be the associated wear and / or the bouncing of the anchor on the anchor armature, as a result of which the total operating time is increased. It is therefore an object of the invention to keep the fall time of the armature short until it is at rest. According to the invention this goal is achieved by e.g. Hydraulic damping of the armature return movement reached in the last part of this movement.

FIG. 9 shows an exemplary embodiment of the injection pump, which essentially has the structure of the injection pump 1 according to FIG. 1. For the hydraulic damping, a cylindrical projection 10a is formed centrally on the back of the armature 10 in the manner of a piston-cylinder arrangement, which in the last section of the armature return movement suitably enters a pocket cylinder bore 11b in the base 11a which on the stop surface 11a for the armature 10 is formed in the housing 8. Longitudinal grooves 10b are formed in the armature 10, which connect the armature-back space 11 to the armature-front space 11. In the space 11 there is a medium, for example air or fuel, which can flow through the grooves 10b when the armature 10 moves. The depth of the blind cylinder bore 11b corresponds approximately to the length of the projection 10a (dimension Y in FIG. 12). Because the projection 10a can dip into the pocket cylinder bore 11b, the armature return movement in the last section is greatly delayed, as a result of which the desired hydraulic damping of the armature return movement is brought about by displacing the medium from the space 11b. 10a shows a variant of the hydraulic damping. In this exemplary embodiment too, the pump chamber 11 through which the delivery piston 14 passes is connected in front of the armature 10 to the space 11 adjoining the rear side of the armature, specifically through holes 10 d that open into a central overflow channel 10 c in the region of the rear side of the armature. A central pin 8a of a shock absorber 8b protrudes with its conical tip 8c in the direction of the mouth of the overflow channel 10c, reaches through a hole 8d in the bottom 11a at the rear, which opens into a damping space 8e, and ends in the damping space with a ring 8f, which has a larger diameter has than the hole 8d. A spring 8g supported on the bottom of the damping space presses against the ring 8f and thus the pin 8a into its rest position (FIG. 10a). A channel 8h connects the damping space 8e to the rear armature space 11. The channels 10c and 10d allow the armature 10 to move almost without resistance during the acceleration phase.

The damping device 8b is ineffective in the acceleration movement of the armature 10, so that there is no impairment of the lifting phase. In the return movement ^'meets the mouth of the overflow channel on the cone apex 8c and is sen verschlos¬, so that the flow is chen through the channels 10c and lOd unterbro¬. The armature 10 presses the pin 8a against the spring force and against the medium in the room 8e, which is also in the room 11 and flows out through the channel 8h into the room 11. The flows and spring forces are selected so that optimal damping is guaranteed.

Instead of the channel 8h, a displacement bore 8i can be arranged centrally in the pin 8a according to FIG. 10b, through which the damping medium can be pressed into the overflow channel 10c.

According to a further advantageous embodiment of the injection device according to the invention, it is provided that the energy stored in the return spring 12 of the armature 10 is used to advantage in the return movement of the armature 10. According to the invention, this can take place, for example, in that the anchor at the default. Pumping device operated, which can be used for the fuel supply of the _Ininjektionvorrichtung to stabilize the system and to prevent bubbles or as a separate oil pump for engine lubrication. 11 shows a corresponding exemplary embodiment of an oil pump 260 connected to the fuel injection pump 1.

The fuel injection device shown in FIG. 11 is otherwise designed in accordance with FIG. 4, that is to say has a fuel inflow and outflow control element for controlling the first partial stroke of the delivery piston 14. The oil pump 260 is connected to the rear bottom 11a of the pump housing 8. Specifically, the oil pump 260 comprises a housing 261 which is connected to the housing 8 of the injection pump and in the pump chamber 261b of which a pump piston 262 is arranged, the piston rod 262a of which projects into the working chamber 11 of the armature 10 The piston 262 is acted upon by a return spring 263 which is supported on the housing base 261a in the region of an outlet 264.

In addition, the pump chamber 261b of the housing is connected to an oil reservoir 266 via an oil supply line 265. A check valve 267 is used in the oil supply line 265, the structure of which is similar to the valve 16 in FIG. 1.

The oil pump 260 works as follows. If the armature 10 of the injection pump 1 is moved in the direction of the injection nozzle 3 during its working stroke, the volume of the pump chamber 11 in the housing 8 behind the armature 10 is increased, as a result of which the oil pump piston 262 is moved in the direction of the armature 10 and finally by action the return spring 263 is brought into its rest position. Oil is sucked in from the reservoir 266 into the working space 261b of the oil pump 26.0 via the valve 267. During the return movement of the armature 10 of the pump 1 in the direction of its stop 11a, the oil pump piston 262 is pushed into the oil pump chamber 261b at least over part of the return path of the armature 10. It is by the Pump pressure closes the valve 267 and oil is discharged via the outlet 264 in the direction of arrow 264a from the oil pump and pressed to the locations of the engine to be supplied with oil.

The oil pump 260 can alternatively also be used as a fuel back pressure pump, wherein the fuel can be supplied to the valve device 70. It is advantageous here that the pump 260 can generate a static pressure in the fuel supply system which prevents vapor bubbles from forming e.g. counteracts heating of the overall system.

In addition, the inventive design of the additional pump 260 on the pump 1 causes the armature 10 to be damped quickly, so that the armature 10 does not rebound at the stop 11a. ^'

Figures 12a and 12b show a particularly effective and simple damping device. The structure of the pump device 1 is the same as that shown in FIG. 9. The blind cylinder bore 11b according to FIG. 12a is larger in diameter than the diameter of the cylindrical projection 10a. The projection 10a is surrounded by a sealing lip ring 10e projecting in the direction of the blind cylinder bore 11b and made of an elastic material which fits into the blind cylinder bore 11b. An insertion bevel at the mouth of the blind cylinder bore 11b facilitates the entry of the lips of the sealing lip ring 10e into the blind cylinder bore 11b. This damping device provides good damping when the armature 10 strikes and does not hinder the acceleration stroke of the armature. The elastic damping element 10 with axially parallel projecting sealing lips plunges positively into the pocket cylinder bore 11b during the return stroke of the armature 10 and rests against the inside wall of the pocket cylinder bore 11b in a sealing manner to the outside.

The blind cylinder bore 11b according to FIG. 12b is also larger in diameter than the cylindrical projection 10a. A sealing ring 10f made of elastic material sits positively on the wall of the blind cylinder bore 11b and points in the region of the Mouth inward-facing sealing lips 10g. The cylindrical projection 10a is plunged into the elastic sealing element 10f, the sealing lips 10g being pressed against the cylindrical projection 10a as a result of the outflowing damping medium, so that particularly good damping of the armature 10 is achieved.

FIG. 13 shows a likewise compact design of the electrically operated reciprocating pump according to the invention with an integrated stop valve. In this case, a coil 201 is arranged in a cylindrical, multi-part housing 200 in an interior 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 into a tank-side and a pressure line-side interior region by a ring 203 which extends radially inwards. On the 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 passing 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 expanded 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.

On the part of the piston 205 located in the tank-side interior area of the interior 202, a pump cylinder 210 of the reciprocating piston pump is seated in a form-fitting and slidable manner 214 is pressed against a ring step 213 in the interior 202, a face 214 protruding valve stub 215 protrudes a little 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 disc 218 of which is arranged at a distance from the end face of the piston 205 in a short bore extension and the tappet stem 219 of which is narrowed Bore 217a in valve stub 215, which supports itself against the inner wall of bore 217a, extends through and projects into narrowed interior space 202a.

At the free end of the plunger style 219, a plate 220 is expediently fastened, which has holes 221, the function of which is explained 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 below is explained. A helical spring 224 stabilizes this position of the tappet valve in the rest position of the reciprocating pump shown, 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.

From the bottom surface 222, 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 in the tank direction by a coil spring 228, 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 pressure on the tank connection side 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 13 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 from the bore 217 or the tappet plate space in the direction of the interior 202a. The accelerated movement ends abruptly when the valve seat 223 strikes the valve plate 218, so that the stored energy of the cylinder 210 is transmitted to the fuel located in the tappet antechamber. The valve 208 is opened and the pressure on the fuel located in the bore 207 or in the pressure line is propagated, as a result of which fuel is sprayed off through the injection nozzle. If the excitation is not yet switched off, fuel is sprayed off as long as the cylinder is being 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. Coming from the tank, 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. After the excitation has been switched off is the cylinder by the spring 211 in its rest or out The tappet stem 219 abuts against the bottom wall 222 and the tappet valve is opened so that fuel can flow through the gap between the tappet stem and the bore 217a into the tappet disc antechamber 217. The valve 208 remains closed. It acts as a standing pressure valve and maintains a standing 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 temperature, so that bubbles do not form can be.

In the embodiment of the injection pump shown in FIG. 14, which is the same as the embodiment in FIG. 13, which is why the same parts are provided with the same reference numerals, the piston 205 is formed in one piece with the end wall 200d and the auxiliary pressure valve 208, 209, which is shown in FIG is accommodated in a pipe socket 208a, 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 Boh ¬ stanchions 234 lead to the enlarged bore area of bore 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. In this embodiment of the invention, the tappet valve 218, 219 is not spring-loaded. It works due to inertia forces, the plunger stem being seated approximately in a form-fitting manner in the narrowed bore 217a. In the position shown in FIG. 14, 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. When the armature cylinder 210 is reset, the tappet stem 219 abuts against the plastic block 231, so that the tappet valve returns to the starting position shown.

The hole extension expediently forms the hole

217, in which the tappet plate 218 is received, an annular step 235 on the pressure line side, which in the rest position of the tappet valve is only a short distance in front of the tappet plate 218 and against which the tappet plate 218 bumps if the tappet is caused by inertia during 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. Recesses 235a are made in the end face of the ring step 235, which ensure an unimpeded flow of the fuel. In this way, the rest position of the tappet valve is ensured with simple means.

During the acceleration of the armature cylinder 210 in this embodiment of the injection pump, fuel flows from the pressure line-side interior 202 via the grooves 216 into the tank-side interior 202 and from the bores 207, 217 through the recesses 235a past the 3-oar plate 218 and through the valve seat opening into Bores 235 also into the tank-side interior 202. The displacement of the fuel is suddenly interrupted by the closing of the tappet valve 218, 219, as a result of which the intended pressure surge is effected. The plunger valve opens during the return movement of the armature cylinder 210

218, 219 and the fuel flows in the opposite direction. So that the starting movement of the armature cylinder 210 from the rest position cannot be impaired, it is expediently provided that 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, rest on the surface of the plastic block 231 and provide the distance "A", so that there is no disruptive 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 occur. Such support webs can be arranged for the same purpose on the end face of the plunger stem 219 (not shown). In addition, the distance "A" is chosen to be so small that damping takes place during the return stroke by squeezing fuel out of the gap "A".

The embodiment of the reciprocating piston pump according to FIGS. 14 and 15 can be provided with a simply constructed, effective armature damping device, which is shown in FIG. 16. 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. In the surface of the plastic block 231, 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. During the return movement of the armature cylinder 210, the flange ring 219a is carried along with 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 onto which a connector 237 with a through-bore 238 is placed on the outside. Through the bore 236 and the drain port 237, e.g. during the starting phase of the pump or the motor, 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. Through the outlet 236, 237, fuel can also be flushed during the injection activity of the pump, thereby dissipating heat, and blistering can be avoided.

A pressure spring 238, which is supported on the end wall 200b, is expediently arranged on the inner wall of the pressure line-side interior 202, against which an end ring surface 239 of the armature cylinder only abuts when the armature cylinder 210 accelerates when there is a large stroke is initiated for a large amount of fuel to be sprayed. The spring is compressed. During the return movement of the armature cylinder 210, the spring 238 releases its stored spring force to the armature cylinder 210, so that it moves correspondingly accelerated into the rest position.

In the reciprocating pumps described below with reference to FIGS. 17, 18, 19, the cylinder 210 acts as a piston-like anchor element which is guided in the inner cylinder 200b in a liquid-tight manner.

An injection pump 1 similar to the injection pump shown in FIG. 13 is shown in FIG. 17, 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 is screwed into the interior 202 on the injection valve side. The valve cap has a central injection nozzle hole 3d. In its rest position, 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 at another end against an intermediate wall 241 arranged in the armature cylinder bore 217, which divides the bore 217 into an injection nozzle and a tank side Section. 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 injection nozzle Bore 217 in the tank-side interior 202, the central region of the armature cylinder 210 being seated positively and almost liquid-tight 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.

17 works as follows. If the armature cylinder 210 is initially accelerated without resistance from the rest position shown, fuel flows via the bore 242 into the tank-side space of the bore 217 and from there into the space 202a, the valve 229 remaining closed. In addition, fuel flows through the bore 243 from the injection valve-side space of the bore 217 into the tank-side interior 202 and from there - since the armature cylinder 210 has lifted off the end ring surface 213 - also into the space 202a through the gap formed thereby. As soon as the tappet valve 218, 219 is gripped by the valve seat, the desired pressure surge occurs in the interior 202 on the injection valve side. 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 sprayed off. Simultaneously, a negative pressure which also acts on the piston 205, but is much smaller amounts than the Fader¬ force of the spring 240 so that the piston so far remains unbeein¬ influ- created in the space 202a and ^■ tank-side interior 202nd 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.

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. 18. This embodiment is similar to that of FIG. 17, which is why the same parts are used same reference numerals are marked.

In this case, the 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 bore 217, in which tappet plate 218 of tappet valve 218, 219 is received. At the free end of the tappet stem 246 there is fastened a ring 248a with holes or edge recess 248 against which ... injection valve supports a compression spring 250 on the other side, which rests on the end wall 200d of the housing 200 or on the valve cap 3b. It is essential 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.

In contrast to the embodiment according to FIG. 17, this injection pump, which has no 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. The plunger plate 218 then hits the plunger stem 246 after a further stroke "H" and holds the valve 244 open.

An embodiment of the injection pump 1 according to the invention which is similar to the embodiment shown in FIG. 18 is shown in FIG. 19, the same parts again being identified by 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 which has a central bore 217d and which divides the bore 217 into an injection valve-side and a tank-side region which via the bore 217d stay in contact.

In this version of the injection pump 1, the spring 251 supports the opening of the valve 244, as in the case of the embodiment according to FIG. 18, 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.

With the aid of the injection device according to the invention, an engine start without a battery and an engine emergency run without a battery can be operated. This possibility is described in more detail below with reference to FIGS. 20, 21, 22.

The electrically driven or electronically controlled injection requires sufficient electrical energy for starting and running. In the event that the electrical energy is not available in sufficient size, the possibility according to the invention should be created to start engines with the injection according to the invention even without electrical energy, for example by means of a hand crank drive. The necessary fuel is provided by an auxiliary device, as explained in more detail below. If the engine reaches a speed at which the generator provides sufficient energy, the auxiliary fuel device is switched off according to the invention and the injection is controlled electrically or electronically, the normal case. corresponding.

There are engines that are started without electrical energy, e.g. by hand or kick start device. These include small motors from hand tools, two-wheeled vehicles or outer borders. This starting device is required because there is no battery to start and / or run. In addition, engines should be able to be started without electrical energy, for example even when the battery is discharged.

According to the invention, the possibility of starting engines without electrical energy by means of an auxiliary device is achieved in that the fuel supply condition present on each engine, for example the inlet gradient or the pressure of the fuel feed pump at starting speed, is used. The fuel is fed directly to the intake manifold or the overflow in two-stroke engines or a metering device. Then the engine reaches a speed at which the generator has sufficient energy for the Provides injection, a valve blocks the direct fuel supply to the engine, the fuel is fed to the injection device and this then takes over the fuel supply to the engine.

20 shows an arrangement according to the invention for supplying fuel to an engine 500. In this case, after a fuel back pressure pump 501, which is connected on the suction side to a fuel reservoir 502, a branching of the fuel supply to the engine is provided. In the de-energized state, an injection device 504 connected to a generator 503, which is constructed in accordance with one of the above exemplary embodiments, is inactive, and an, for example, electromagnetically operated control valve 505 is opened for the fuel supply to an atomizer 506 on the engine 500.

When the engine 500 is started, the fuel pressure supplied by the pre-pressure pump 501 is supplied to the atomizer 506 located on the engine 500 via the opened control valve 505. The flow resistance of the control valve 505 and / or the atomizer 506 is dimensioned such that the supply of pressure from the admission pressure pump 501 at the starting speed covers the fuel requirement for the start. When the generator 503 coupled to the engine reaches a speed at which the energy required for the injection device 504 is covered, an injection control 507 becomes active, which is also fed by the generator 503 and is connected to the injection device 504 via a control line. For this purpose, the control valve 505 is closed by means of a current signal, so that no more fuel can be fed directly to the engine. At the same time, the injection device 504, controlled by the injection control 507, takes over the injection via the injection nozzle 508.

A hand pump 509 present on many motors can optionally also be used during the starting process for the direct fuel supply to the motor via the atomizer 506. The Hand pump 509 is arranged in the connecting line 511 from the pump 501 to the control valve 505. The control valve 505 is controlled by the injection control 507 via a control line 510.

FIG. 21 shows a modification of the arrangement according to FIG. 20, in which the control valve 505 is arranged in the injection line 511 between the injection device 504 and the injection nozzle 508. The function of stormless starting corresponds to the function explained above with reference to FIG. 20.

In order to ensure that the fuel flows through without pump support of the injection device 504, the flow resistance of the injection device 504 is kept small. It is advantageous that the injection device 504 and the injection line 511 can be vented without problems. If the injection device be vented 504, the Steuer¬ is valve 505 via a switch 512 in the direction of ^'' he injection control 507 to the control valve 505 gemaci dead ... if it does not er¬ followed by the injection control 507. As a result, the control valve 505 is opened in the direction of the atomizer 506, and the air in the system can escape with simultaneous pumping, for example with the form pressure pump 501 or the hand pump 509.

22, the engine emergency operation according to the invention without battery will be described in more detail below.

The arrangement shown in FIGS. 20 and 21 can also be used for the emergency operation of the engine, in which, for example due to failure of the generator, there is insufficient energy available for the injection control and the injection device. According to the invention, a quantity variation of the fuel takes place through a metering device, for example through an adjustable throttle in the control valve coupled to the throttle valve in the air intake pipe, which allows control of the engine load in a makeshift manner. 22 shows a suitable embodiment of the control valve or the metering valve 505 in FIGS. 20 and 21. The control valve 505 has a housing 520, into which a coil 521 is inserted, which serves to drive an armature 522, which is shown in FIG a bore 523 of the housing 520 is slidably mounted and in its rest position is pressed by a return spring 524 against an adjustable stop 525 arranged in the housing 520, to which a cable pull 526 is connected outside the housing. Longitudinal grooves 527 are formed in the armature 522, which permit fuel in the bore 523 to communicate between the front and rear of the armature .522. The piston-shaped stop 525 passes through the housing end wall 520b and is biased in the housing 520 by means of a spring 528 with respect to the housing end wall 520b.

A metering piston 527 is formed uniformly with the end face of the armature 522 opposite the stop 525. This end face is also acted upon by the return spring 524, which is supported at the other end against the end wall 520a of the housing 520. The metering piston 527 protrudes with a conically tapering tip end into the delivery line 511, from which a connecting line 511a branches off to the atomizer 506.

The cable pull 526, which is connected to the stop 525 biased under spring force against the armature 522, is connected to the throttle valve 530 (see FIGS. 21, 22). The throttle valve position is thereby transmitted directly to the stop 525.

The function of the control valve 505 is as follows. In the de-energized state of the coil 521, the armature 522 and the metering piston 527 rest against the stop 525 by the return spring 524. The fuel can flow from the feed pump 501 through the feed line 511 to the atomizer 506. If the control valve 505 is excited by the control device, the armature 522 presses the metering piston 527 against the force of the spring 524 to the extent Delivery direction until the inlet cross section 531 of the delivery line 511 is closed.

If the engine is operated in emergency mode without injection, the control valve 505 is de-energized and thus the inlet cross section 531 in the line 511 to the atomizer 506 is released. Corresponding to the throttle valve position, the conical metering piston 527 is pressed more or less far into the bore of the inlet cross section 531 via the armature 522 through the stop 525. The coupling to the throttle valve 530 is chosen so that the cross-section 531 opens more with increasing opening of the throttle valve 530. In the idle position of throttle valve 530, a minimal gap remains at cross section 531, which allows the amount of idle fuel to pass to atomizer 506.

23 shows a preferred circuit for controlling the armature excitation coil of the injection pumps according to the invention, which ensures optimum acceleration of the armature.

It is known to dose the amount of fuel to be sprayed, for example in a time-controlled manner. A purely time-based control has proven to be disadvantageous, however, because the time window that results between the minimum and maximum amount of fuel to be sprayed is too small to differentiate the quantity spectrum required in engine operation and to control it in a reproducible manner. However, a sufficiently differentiable quantity metering can be achieved via the pure intensity control of the current flow according to the invention.

In the case of the electromagnetic drive of the fuel injection devices according to the invention, the excitation, that is to say the product of the number of turns of the coil and the current strength of the current which passes through the coil, is particularly decisive for the electromagnetomechanical energy conversion. This means that an exclusive control of the current amplitude allows the switching behavior of the drive magnet to be independent of the effects of coil heating and a fluctuating supply voltage to be clearly defined. In this way, such a control system takes into account in particular the electrical voltage conditions, which usually fluctuate strongly in motors, and the different temperature conditions.

23 shows a two-point control circuit according to the invention for the current amplitude of the current controlling a pump drive coil 600. The drive coil 600 is connected to a power transistor 601 which is connected to ground via a measuring resistor 602. A comparator 603 with its output is applied to the control input of transistor 601, for example to the transistor base. The non-inverting input. the comparator is acted upon by a current setpoint which is obtained, for example, by means of a microcomputer, and the inverting input of the comparator 603 is connected to the side of the measuring resistor which is connected to the transistor 601.

In order to control the energy flow in the drive coil 600 independently of the supply voltage, the current absorbed by the coil 600 is measured by the measuring resistor 602. If this current reaches the limit value specified by a microprocessor as the current setpoint, the comparator switches off the current for the coil 600 via the power transistor 601. As soon as the actual current value falls below the current setpoint, the transistor switches the coil current on again via the comparator. The current rise delay caused by the inductance of the coil 600 prevents the maximum permissible current from being exceeded too quickly.

The next switching cycle can then begin, and this clocking of the coil current of the coil 600 takes place as long as the reference voltage supplying the current setpoint is present at the non-inverting input of the comparator 603.

The circuit represents a clocked current source, the clocking only after the microprocessor has uses the current setpoint. The energy and thus the quantity control of the pump device 1 can take place with this circuit in combination of the duration and / or the amount of the reference voltage provided by the microprocessor.

24, 25 and 26 show particularly advantageous embodiments of the injection nozzle (e.g. nozzle 3) for the injection device according to the invention.

This injection nozzle comprises a valve seat tube 701, at the free lower end of which the membrane 70 is arranged, if appropriate a jet-shaping pin insert 702 (which is seated in a central hole in the membrane 704), a nozzle holder 703, a membrane plate 704 biased towards the valve seat, one Snap ring 705, a pressure line 706 which opens on the valve seat side into an annular channel 708 which is open to the membrane 704 and is covered by the membrane, a pressure screw 707, a seal 709 for the nozzle holder 703 and a receptacle 710 for the nozzle holder 703 .

With the membrane flat seat nozzle shown in FIGS. 24, 25 and 26 with nozzle pin 702 (FIG. 25) and without nozzle pin 702 (FIG. 26), good fuel atomization is achieved on the surface of a curved cone jacket. The shape and dimensions of this jacket include dependent on the dimensions and design of the outlet opening in the membrane (FIG. 25) and can, if necessary, be additionally adapted to the requirements of engine operation with the known functional advantages with the aid of a straightening pin or throttle pin.

The valve works almost without moving masses and is characterized by a specially designed metal membrane that works with a fixed flat valve seat. The membrane - at the same time because of the preload of the valve spring - can be preloaded against the direction of opening (eg by arching) by means of suitable, defined and permanent deformation. This allows fuel atomization at low pressures the nozzle opening which is formed by the central hole in the membrane 704, for example at low speeds and small injections (in low part-load operation). Machining the nozzle hole (rounding the edges, etc.) is easily possible from both directions.

In order to reinforce the good closing effect on the valve of the injection nozzle opening outwards, the seat ring width of the flat seat (FIG. 25) can be coordinated with the pretension of the membrane plate. The correct choice of the dimensions of the lower groove in the valve seat contributes to this, which results in the force acting on the membrane at a given standing pressure of the fuel in front of the valve seat. On the other hand, the membrane is effectively cooled by the fuel stored in the ring groove or flowing through it.

The nozzle requires no lubrication and is therefore particularly suitable for petrol, alcohol and mixtures thereof. Because of the mode of operation - there is no volume downstream of the valve seat - comparatively lower hydrocarbon emissions from the engine are to be expected in this nozzle than with inwardly opening nozzles.

The nozzle consists of a few parts, so its mass production, maintenance, inspection and part replacement is very simple and inexpensive.

Fuel supply devices for fuel injection systems are flushed with fuel to cool them and to remove vapor bubbles during operation. This means that the fuel delivery pump provides a larger amount of fuel than is required by the engine. This additional quantity is returned to the tank via a line and is used for heat dissipation and for the removal of fuel vapor bubbles. Vapor bubbles occur during engine operation due to the effects of heat and can disrupt or even prevent the function of the injection system. A steam engine can also be used to restart the low-power engine. difficult or even prevented.

In certain engine applications, e.g. as an outboard motor on boats, a return line to the tank is not permitted by law for safety reasons.

According to a further embodiment of the invention, a fuel supply device with a fuel injection device according to the invention is therefore designed without a return line to the tank, although heat and steam bubbles can still be removed.

The invention solves this problem by using a second fuel pump, a gas separation chamber with a floating valve and a cooler. This arrangement can be attached directly to the engine and thus avoids fuel lines under pressure outside the engine or the engine capsule. This is enough to meet the legal safety regulations.

27, this fuel supply device is explained in more detail below by way of example.

A pump 801 sucks the fuel 802 from the tank 803 and feeds it through a fuel line 804 to a gas separation chamber 805. The gas separation chamber 805 has a float 806 which operates a ventilation valve 807 which acts on a gas discharge line 808 arranged in the ceiling area above the liquid level 805a.

A fuel line 809 is branched off from the bottom of the gas separation chamber 805 and is connected to a pump 810 and leads to an injection valve 811 according to the invention, which is connected via a fuel line 812 to the gas separation container 805, which opens into the gas separation container 805 above the liquid level 805a. As a result, a pressure regulator 813 and a cooler 814 are seated in the fuel line 812 starting from the injection valve 811. The new fuel supply device for a fuel injection device according to the invention functions as follows: The pump 801 sucks the fuel 802 out of the tank 803 and feeds it to the gas separation chamber 805 until the vent valve 807 is closed by the float 806. The pump 810 takes the fuel from the bottom of the gas separation chamber 805 and builds up the pressure required for the respective injection system upstream of the pressure regulator 813. In terms of its delivery characteristics, the pump 810 is designed such that it applies the amount of fuel required for cooling and flushing the injection valve 811 and supplies it to the gas separation chamber 805 via the cooler 814. If steam bubbles 805b are now discharged into the gas separation chamber 805, the fuel level 805a will decrease, the float 806 opens the vent valve 807 until the pump 801 has delivered to the original level 805a. The vent valve 807 is connected to the air intake pipe 808 of the engine, so that the fuel vapors drawn from the air intake pipe cannot get unburned into the environment.

Claims

1. Fuel injection device which works according to the solid-state energy storage principle, wherein a piston element guided in a pump cylinder of a piston pump driven by an electromagnet piston parts of the fuel to be sprayed off during an almost resistance-free acceleration phase, during which the piston element kinetic Energy is stored, displaced in the pump area before spraying and the displacement is suddenly stopped by means which interrupt the displacement, so that a pressure surge is generated in the fuel located in a closed pressure chamber by the stored kinetic energy of the piston element being directly on the one located in the pressure chamber Fuel is transmitted, and wherein the pressure surge is used for spraying fuel through an injection nozzle device, characterized in that the displacement-interrupting means generating the pressure surge are external are arranged above the leading liquid-tight contact area between the reciprocating piston element and the reciprocating piston cylinder of the reciprocating piston pump.

2. Apparatus according to claim 1, characterized in that the means for interrupting the displacement or for generating the pressure rise are designed as a device having a stop means (6, 50, 70, 90, 125, 218/223) aus¬.

3. Device according to claim 1 and / or 2, characterized in that the sling means (e.g. 37) is designed to be position-adjustable.

4. Device according to one or more of claims 1 to 3, characterized in that a volume storage element (6) is provided for the displacement of fuel during the acceleration phase.

5. The device according to claim 4, characterized in that it has an electromagnetically driven reciprocating pump (1) which is connected via a delivery line (2) to an injection nozzle device (3), with an intake line (2) from the delivery line (2). 4) branches off, which is connected to a fuel reservoir (5) and wherein the volume storage element (6) is connected to the delivery line (2) via a line (7).

6. The device according to claim 5, characterized in that the pump (1) has a housing (8) in which an annular coil (9) is mounted, wherein in the region of the coil passage an armature (10) is arranged, which is designed as a cylindrical body and is guided in a housing cylinder which is located in the area of the central longitudinal axis of the ring coil (9) and is pressed by means of a compression spring (12) into an initial position in which it rests on the bottom (11a) of the housing cylinder, A delivery piston (14) is attached to the end face of the armature (10) on the injection nozzle side, which plunges relatively deep into a cylindrical fuel delivery chamber (15), which is arranged coaxially to the housing cylinder and is in transmission connection with the pressure line (2). stands.

7. The device according to claim 5 and / or 6, characterized in that a check valve (16) is arranged in the suction line (4).

8. The device according to one or more of claims 4 to 7, characterized in that the storage element (6) has a housing (22), in the cavity of which a diaphragm (23) is stretched as the organ to be displaced, which from the cavity a Drucklei ¬ separates fuel-filled space _, and divides the cavity into two halves in the relaxed state, which are sealed against each other by the membrane, an empty space is arranged on the side of the membrane facing away from the line (7), which has a vault-shaped GE wall (22 a) as a stop means for the membrane (23).

9. The device according to claim 8, characterized g e k e n n z e i c h n e t that on the line (7) facing away from the membrane

(23) a spring acting on the membrane in the empty space

(24) is arranged, which acts as a return spring for the membrane (23). .

10. The device according to one or more of claims 5 to 9, characterized in that a check valve (16a) is arranged in the pressure line (2) between the injection valve (3) and the pressure chamber in front of the branches (4, 7), that forms a storage space in the injection valve-side space for maintaining a certain static pressure in the fuel.

11. The device according to one or more of claims 4 to 7 and 10, characterized in that as a displacement element for the storage element (6) Storage piston (31) guided in a cylindrical housing (30) connected to line 7 is used, the cylinder (30) providing an empty volume (33c) into which the piston (31) receives the fuel can be ousted.

12. The apparatus according to claim 11, characterized in that a drain hole (32) is arranged in the region of the empty space volume (33c).

13. The apparatus of claim 11 and / or 12, characterized in that a compression spring (34) is clamped in the void volume (33c), which presses the piston (31) into its rest position against a pressure line-side housing wall (33a).

14. The device according to one or more of claims 11 to 13, characterized in that an axially adjustable stop bolt (37) for the piston (31) is arranged in the void volume (33c), which passes through the housing wall and outside the housing with a Adjustment means is connected.

15. The device according to one or more of claims 1 to 7 and 10, characterized in that the fuel feed valve (16) is also designed as a storage element valve (50).

16. The apparatus according to claim 15, characterized in that the valve (50) has a cylindrical housing (51) in which a through bore (52) is made, which has a pressure line side section (53) and a suction side section (53b ), whereby is formed between a radially expanded valve chamber (54) which receives a shut-off valve element (55) which consists in one piece of a circular disc (56) of large diameter and a circular disc (57) of small diameter, the circular disc (57) on the side of the bore section

(53) is arranged and wherein a valve body return spring (58) the valve element in the idle state against a pressure line end face (59) of the valve chamber

(54) presses, which is supported on the one hand on the circular disc (56) and on the other at the bottom of an annular step (60) which is arranged centrally in the end face (61) opposite the end face (59) of the valve chamber (54), so that the Circular disk (56) can come into sealing contact with the end face (61) of the valve chamber (54) and the bore section (53) in connection with the valve chamber (54) via grooves or grooves (62) arranged in the housing wall (51) ) stands, which are expediently widened in the direction of the valve chamber (54).

17. The apparatus of claim 15, g e k e n n z e i c h n e t by an electromagnetically controlled valve (70).

18. The apparatus according to claim 17, characterized ^'in that the valve (70) in a valve housing (77) has a ring coil (78), in the interior of which a cylinder bore (74) is provided, in which an armature ( 73), which is connected to a spring-loaded valve plate (72) and has at least one bore (75) running transversely to the longitudinal extension of the armature in the region of the valve plate, the armature (73) being connected to the plate (72 ) pressing spring (76) is pressed into an end position on the pressure line, in which the fuel via the bores (75) and (74) and the pressure line opening (71) with the fuel of the pressure chambers (15, 2) communicates.

19. The apparatus according to claim 15, characterized by an integral storage element supply valve device (90) which has a housing (91) into which a Mittenlängsboh¬ tion (92) is introduced, which ends at one end via an opening (93a) in the pressure line ( 2) and at the other ends in a cylindrical valve chamber (93), with channels (94) leading from the bore (92) to the valve chamber (93) and the valve element being in two parts and a cylinder (93) guided in the valve chamber (93) 95) comprises a piston in its cylindrical through-center bore

(96) is displaceably guided and wherein in the outer surface of the cylinder (95) axially parallel grooves

(97) and the cylinder (95) is pressed into its rest position by a spring (98), in which it rests with its one end face on the tank-side bottom of the valve chamber (93), into which one comes from the fuel tank Fuel supply line (99) opens, and in the bore for receiving the piston (96) a spring (100) sits on the tank side, which presses the piston (96) against the pressure line side bottom of the valve chamber (93), so that the bore (92) is covered, a space (95a) for the piston (96) being formed in the tank-side interior of the cylinder (95).

20. The device according to one or more of claims 1 to 7 and 10, characterized in that the storage element (6) is constructed in a unitary manner with the delivery piston (14) of the reciprocating piston pump (1).

21. The apparatus according to claim 20, characterized in that a storage piston (80) is used as the storage element, which in a pressure line-side first central longitudinal axis a bore (14b) of a stepped bore (14a) passing centrally through the piston (14) and the armature (10) is pressed against a stop on the pressure line side by a spring (81), the piston (80) in the rest position with its one end face in protrudes the pressure chamber (15) and the bore section (14b) in the delivery piston (14) receiving the storage piston (80) continues after a step (14c) towards the armature (10) in a further stepped bore section (14d), at the step (14e ) a pressure spring (81) is supported, which presses against the armature-side end face of the piston (80).

22. The apparatus according to claim 4, characterized in that a tank-side hydraulic valve together with the pump (1) and the pressure line (2) are housed in a common housing (121) and a hydraulically controlled fuel feed valve seated in the fuel supply line ( 122), which closes automatically due to the Bernoulli effect at a certain flow rate.

23. The device according to claim 22, characterized in that the fuel passes through a gap (123) in a Ventil¬ space (124) of the valve (122) in which between a valve cone (125) and the associated valve seat a schma¬ ler An annular gap is left, which can be adjusted by appropriate design of a spring (126) acting on the valve cone (125).

24. The apparatus of claim 22 and / or 23, characterized in that the pressure line (2) leading to the injection nozzle is connected to the outlet of a check valve (127), which is also structurally combined in the housing (121) and arranged above that the fuel path to the injection nozzle 3 leads.

25. The device according to claim 24, characterized in that the check valve (127) has a valve cone (128), which is pressed by prestressing a spring (129) against an associated valve seat, the spring (129) being designed such that the valve (127) is closed when the pressure in the direction of the pressure line (2) is below the value which leads to an emission of fuel via the injection nozzle (3) which is indirectly connected to the valve (127).

26. The device according to one or more of claims 1 to 25, g e k e n n z e i c h n e t by a hydraulic damping device for the anchor element

(10) the reciprocating pump.

27. The apparatus according to claim 26, characterized in that the hydraulic damping device is constructed in the manner of a piston cylinder arrangement, with a cylindrical projection (10a) being formed centrally on the armature (10), which in the last section of the armature return movement into a pocket cylinder bore ( 11b) fits in the base (11a) of the cylinder, grooves (10b) extending in the longitudinal direction being arranged in the armature (10) which connect the space on the back of the armature with the space on the front of the armature in the pump cylinder.

28. The apparatus according to claim 26, characterized in that the pump chamber (11), through which the delivery piston (14) passes, is connected in front of the piston (10) to the space (11) adjoining the armature back side by bores (lOd) which in Area of the back of the armature in a central overflow nal (10c) open, wherein a central pin (8a) of a shock absorber (8b) with a cone tip (8c) protrudes towards the mouth of the overflow channel (10c).

29. The device according to claim 28, characterized in that the central pin (8a) engages rearwards through a hole (8d) in the bottom (11a) which opens into a damping space (8e), the pin (8a) in the damping space with a ring (8f) ends, which has a larger diameter than the hole (8d), and wherein a spring (8g) is supported on the bottom of the damping space, which presses against the ring (8f), and wherein a channel (8h) Damping space (8e) connects to the rear anchor space (11).

30. The device according to claim 28, characterized in that a continuous displacement bore (8i) is arranged centrally in the pin (8a) and can be pressed through the damping medium into the overflow channel (10c).

31. The device according to claim 26, characterized in that the armature (10) operates a pump device during the return movement, which at the same time ensures a damping device for the armature (10).

32. Device according to claim 31, characterized in that an oil pump (260) is connected to the rear bottom (11a) of the pump housing (8), which has a housing (261), in the pump chamber (261b) of which a pump piston (262) is arranged, the piston rod (262a) of which projects into the working space (11) of the armature (10), the piston (262) being acted upon by a return spring (263) which is located on the housing base (261a) in the region of an outlet (264) supports.

33. Apparatus according to claim 32, characterized in that the pump chamber (261b) is connected via an oil supply line (265) to an oil reservoir (266), a check valve (267) being inserted into the oil supply line (265).

34. Apparatus according to claim 26 and / or 27, characterized in that the blind cylinder bore (11b) is larger in diameter than the diameter of the cylindrical projection (10a) and the projection (10a) or the blind cylinder bore (11b) has a sealing lip ring (10e) or (10d), the sealing lip rings forming the piston seal for the projection (10a).

35. Device according to one or more of claims 1 to 3 and 26 to 34, characterized in that the armature is designed as a pump cylinder (210), the housing interior (202) by a radially inwardly extending ring (203) in one is divided into the tank-side and a pressure line-side interior area, and wherein the pressure line side is set against a ring edge of the ring (203) with a ring bead (204) of a piston (205) of the reciprocating pump (1) which is positively and firmly seated in this interior and which seals the ring opening ( 206) of the ring (203) passes through at a distance and projects into the tank-side area of the interior (202), where it engages in a continuous bore (217) of the armature cylinder (210).

36. Apparatus according to claim 35, characterized in that the piston (205) is penetrated by a through bore (207) which is expanded in the tank-side end region of the piston and there stores a check valve (208) which is supported by a coil spring (209 ) in rieh device tank side for the closed position is pressed against a valve seat (209a).

37. Apparatus according to claim 35 and / or 36, characterized in that the pump cylinder (210) of the reciprocating pump sits on the part of the piston (205) located in the tank-side interior area of the interior (202) in a form-fitting and slidable manner, which ends on one end the coil spring (211) supporting the ring (203) and others on a ring step (212) of the cylinder (210) is pressed with its tank-side end ring surface (214) against a ring step (213) in the interior (202), wherein a valve stub (215) projecting beyond the end ring surface (214) projects a little at a radial distance into the interior (202), which is radially narrowed in this area, and the end line surface of the cylinder (210) on the pressure line side is spaced from the ring (203) and thus a movement space for the cylinder (210) is created.

38. Apparatus according to claim 37, characterized in that 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, and that the pump cylinder (210 ) penetrating, through bore (217) receiving the piston (205) on the tank side supports a plunger valve arranged upstream of the piston 205, the plunger plate (218) of which is arranged at a distance from the end face of the piston (205) in a short bore extension and whose tappet stem (219) passes through the narrowed bore (217a) in the valve stub (215) - supporting itself against the inner wall of the bore (217a) - and protrudes into the narrowed interior (202a).

39. Device according to claim 38, characterized in that a plate (220) is attached to the free end of the plunger stem (219), which has holes (221), the plunger stem (219) protruding a little beyond the plate (220) and against the tank side Bottom surface (222) of the interior (202a) abuts, the plunger stem (219) being chosen so long that the plunger plate (218) is lifted from its valve seat (223) of the narrowed bore (217a) so that a certain gap "X" is formed.

40. Apparatus according to claim 39, characterized in that a helical spring (224) stabilizes the position of the plunger valve in the rest position of the reciprocating pump, in that the spring (224) has one end on the end ring surface (214) of the cylinder (210) and the other against the plate (220).

41. Device according to one or more of claims 35 to 40, characterized in that axially parallel bores (225) extend from the bottom surface (222) into the bottom wall and open into an axial valve chamber (226) in which one of a screw fe the valve plate (229) is pressed in the tank direction against a valve seat (227) and has grooves (230) that can be covered peripherally from the valve seat (227), so that the valve is pressed against the load of the spring (228) by a pressure on the tank connection side can be opened and a passage from the valve chamber (226) to the bores (225) is created.

42. Device according to claim 35, characterized in that the piston (205) is formed in one piece with the end wall (200d) of the housing (200), the stand pressure valve (208, 209) on the pressure line side of the piston (205) in a pipe socket (208a) is upstream and the pressure Covering the mouth of the bore (207) passing through the piston (205).

43. Device according to claim 42, characterized in that the tappet stem (219) is made relatively short and can only protrude over the valve-side end face (214) of the cylinder (210).

44. Apparatus according to claim 43, characterized in that the end ring surface (214) in the region of the end wall (200c) abuts a plastic block (231) mounted there, which has through bores (232) which open peripherally into grooves (233) which are in communication with the tank-side interior (202), bores (234) leading from the tank-side interior (202) to the enlarged bore region of the bore (217) in the cylinder (210) and the bores (232) leading into the tank axial valve chamber (226) open, which is housed in a pipe socket (226a).

45. Apparatus according to claim 44, characterized in that the bore extension of the bore (217) in which the plunger plate (218) is received, pressure line side forms an annular step (235), which is in the rest position of the plunger valve only a short distance from the plunger ¬ plate (218) and against which the tappet plate (218) abuts when the tappet lifts from the valve seat during the return movement of the cylinder (210) and / or the valve from the plastic block (231) during the return movement of the cylinder (210) should be rebounded.

46. Apparatus according to claim 45, characterized in that in the end face of the ring step (235) recesses (235a) are introduced, which ensure an unimpeded flow of the fuel.

47. Device according to one or more of claims 44 to 46, characterized in that the end ring surface (214) is at a short distance from the

Surface of the plastic block (231) is arranged.

48. Apparatus according to claim 47, characterized in that the support webs projecting on the end ring surface (214)

(214a) are arranged.

49. Device according to one or more of claims 35 to 48, characterized by an armature damping device in the free end region of the tappet stem (219), a flange ring (219a) being arranged there which overlaps the end face (214) a little laterally and can rest against the end ring surface (214), and wherein in the surface of the plastic block (231) a recess (231a) corresponding to the flange ring (219a) is made, into which the flange ring (219a) fits approximately in a form-fitting manner.

50. Apparatus according to claim 49, characterized in that the thickness of the flange ring (219a) is somewhat larger than that

Depth of the recess (231a) is executed.

51. Device according to one or more of claims 35 to 50, characterized in that a bore (234) is arranged in the end wall (200d) on the pressure line side, which leads from the interior (202) on the pressure line side to the outside and on which a socket (237) with a through bore (238) is set on the outside, the fuel (anchor cylinder) (210.) or the fuel (running) from the bore (236) and the drain socket (237) during the start phase of the pump 1 or the motor or ) can be pumped out.

52. Device according to one or more of claims 34 to 51, characterized in that on the inner wall of the pressure line-side interior (202) is arranged on the end wall (200b) supportive de compression spring (238a), against which at the . Acceleration of the armature cylinder (210) abuts an end ring surface (239) of the armature cylinder and thereby compresses the spring.

53. Device according to one or more of claims 35 to 52, characterized in that the cylinder (210) acts as a piston-like anchor element in the

Interior (202) is guided liquid-tight.

54. Device according to claim 53, characterized in that a piston (205a) which is partially seated in the armature cylinder bore (217) is axially movable and is part of the spray valve device (3).

55. Device according to claim 54, characterized in that the spray valve device (3) has a valve cap (3b) which is screwed into the end wall (200d) of the housing (200) in a manner reaching into the injection valve-side interior (202), the piston ( 205a) covers the injection nozzle bore (3d) in its rest position with a reduced diameter end face (205b) and the reduced diameter area (205b) with a truncated cone (205c) in passes over the cylindrical part of the piston (205a).

56. Apparatus according to claim 55, characterized in that the piston (205a) in the armature cylinder bore (217) is pressed by a compression spring (240) against the injection nozzle bore (3d), the compression spring (240) at the other end against one in the armature cylinder bore (217) arranged intermediate wall (241) supports, which divides the bore (217) in an injection nozzle side and in a tank side area.

57. Apparatus according to claim 56, characterized in that 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) and that a bore (243) goes through the armature cylinder (210) from the region of the bore (217) on the injection nozzle side into the tank-side interior (202), the central region of the armature cylinder (210) being positive and almost liquid-tight sits on the inner wall of the interior (202).

58. Device according to claim 57, characterized in that the anchor cylinder (210) has grooves in the tank-side region of the interior (202), the groove webs abutting the inner wall of the interior (202) and guides there for the anchor Form cylinder (210).

59. Device according to one or more of claims 35 to 53, characterized in that the injection nozzle (3) is located directly in the end wall

(200d) of the housing (200) and a valve The valve cap (3b) has a valve seat (3c) for a tappet valve (244), the valve disc (245) of which is pulled from the outside against the valve seat (3c) and the tappet stem (246) of which follows the valve seat (3c) Cap bore (3d) passes freely or radially supported by ribs (247) and passes freely through the armature cylinder bore (217) and ends shortly before the enlarged area of the bore (217) in which the tappet plate (218) of the tappet valve (218, 219) is accommodated, a ring (248a) having holes or radial recesses (248) having a hole or radial recesses (248) being fastened to the free end of the plunger stem (246), against which a compression spring (250) is supported on the injection valve side and which is otherwise attached to the end wall (200d ) of the housing (200) or on the valve cap (3b), the armature cylinder (210) only having the through-bore (217a) and no radial grooves, but rather in a form-fitting and liquid-tight manner on the inner wall of the interior (20 2) and the plunger plate (218) hits the plunger stem (246) after a certain stroke during the pumping movement.

60. Apparatus according to claim 59, characterized in that the tappet stem (246) of the tappet valve (244) is shorter and in the rest position of the pump (1) only extends into the end region of the armature cylinder bore (217) on the injection valve, with additional 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 injection valve-side and a tank-side area connected by the hole (217d).

61. Device according to one or more of claims 1 to 60, characterized by an auxiliary starter that connects to an atomizer (506) of the engine (500) from the fuel tank

(502) has fuel-actuated control valve, the flow resistance of which is dimensioned together with that of the atomizer (506) such that the supply of pressure from a pre-pressure pump (501) at the starting speed covers the fuel required for starting even without electrical energy being added to the injector (504) can be.

62. Device according to claim 61, characterized in that after the fuel back pressure pump (501), which is connected on the suction side to the fuel reservoir (502), there is a branching of the fuel supply to the engine, one to a generator in the de-energized state

(503) connected injection device (504), which is constructed according to the invention, in particular one of the exemplary embodiments according to the invention, is inactive and, for example, the electromagnetically actuated control valve (505) for the fuel supply to the atomizer (506) on the engine (500) is open.

63. Apparatus according to claim 61 and / or 62, characterized in that an existing hand pump (509) on the engine is additionally used during the starting process for the direct fuel supply to the engine via the atomizer (506), which in the connecting line (511) from the Pump (501) to the control valve (505) is arranged, the control of the control valve (505) being effected by the injection control (507) via a control line (510).

64. Device according to claim 61, characterized in that the control valve (505) in the injection line (511) between the injection device (504) and the injection nozzle (508) is arranged.

65. Apparatus according to claim 64, by a switch in the line from the injection control (507) to the control valve (505).

66. Apparatus according to claim 64 and / or 65, characterized in that the auxiliary starting device according to the invention is used for the emergency operation of the engine, a metering valve (505) causing a quantity variation of the fuel.

67. Apparatus according to claim 66, characterized in that the metering valve (505) has a housing (520) into which a snule (521) is inserted, which serves to drive an armature (5 _) which is in a bore (523 ) of the housing (520) is slidably mounted and in its rest position is pushed by a return spring (524) against an adjustable stop (525) arranged in the housing (520), to which a cable (526) is connected outside the housing, whereby in Armature (522) peripheral longitudinal grooves (527) are formed, which allow communication of the fuel present in the bore i 523) between the front and the back of the armature (522), and wherein the piston-shaped stop (525) passes through the housing end wall (520b) and is biased in the housing (520) by means of a spring (528) relative to the housing end wall (520b), and with the end face of the armature (52 2) a metering piston (527) is of uniform design, and this end face is also acted upon by the return spring (524), which is supported on the other side against the end wall (520a) of the housing (520), and wherein the metering piston (527) with a tapered tip end protrudes into the delivery line (511), from which a connecting line (511a) to the The atomizer (506) branches off, and the cable pull (526), which is connected to the stop (525) that is biased under spring force against the armature (522), is connected to the throttle valve (530).

68. Device according to one or more of claims 1 to 67, characterized by a circuit for controlling the armature excitation coil (9, 600), which is connected to a power transistor (601) which is connected to ground via a measuring resistor (602), whereby at the control input of the transistor (601), for example at the transistor base, has a comparator (603) with its output, and the non-inverting input of the comparator (603) is acted upon by a current setpoint, for example by means of a microcomputer is obtained and the inverting input of the comparator (603) is connected to the side of the measuring resistor which is connected to the transistor (601).

69. Injection nozzle for a device according to one or more of claims 1 to 68, characterized by a valve seat tube (701) with an end-side ring channel (708), a diaphragm plate (704) prestressed in the direction of the valve seat with a central hole which connects the ring channel ( 708), optionally a pin insert (702) in the hole in the membrane (704), a snap ring (705) and a pressure line (706).

70. Device according to one or more of claims 1 to 69, characterized by a fuel supply device without return line to the tank, a second fuel pump, a gas separating chamber with a floating valve and a cooler being used.

71. Device according to claim 69, characterized by a gas separation chamber (805) into which fuel (802) is pumped from a tank (803) by means of a pump (801) via a line (804), from which a pump ( 810), fuel is fed to an injection valve (811) via a fuel line (809), a line (812) being fed back from the injection valve (811) into the gas separation chamber (805), in which a pressure regulator (813) and a Coolers (814) are arranged, a float (806) being provided in the gas separator (805), which operates a vent valve (807) which is located in a drain line (808) which leads into the gas separation chamber (805). flows.

72. Device according to claim 71, characterized in that the fuel line (812) opens above the liquid level (805a) into the gas separation chamber (805).

73. Apparatus according to claim 71 and / or 72, characterized in that the vent line (808) opens above the liquid level (805a) into the gas separation chamber (805).

74. Power supply device according to one or more of claims 71 to 73, characterized in that the fuel line (804) opens above the liquid level (805a) into the gas separation chamber (805).

75. Device according to one or more of claims 71 to 74, characterized in that all devices of the fuel injection system are arranged in the engine compartment (815) except for the tank (803).