DE102012223920A1 - Rotary piston pump e.g. high-pressure pump for conveying fluid e.g. fuel to internal combustion engine, has an actuator for variable control and/or regulation of bypass channel, to integrate routable volume flow of fluid into channel - Google Patents

Abstract

The pump (1) has an impeller, and a working chamber divided into an inflow workspace and an outflow workspace. The inflow workspace has an inflow duct for introducing the fluid to be conveyed. The outflow channels are opened in outflow workspace for discharging pumped fluid from outflow workspace. A bypass channel is formed from first outflow channel to inflow duct. An actuator for variable control and/or regulation of bypass channel is formed in the housing for integrating the routable volume flow of fluid into the bypass channel. Independent claims are included for the following: (1) a high-pressure injection system for internal combustion engine of motor vehicle; and (2) a method for operating a high-pressure injection system.

Description

The present invention relates to a rotary piston pump according to claim 1, a high-pressure injection system according to claim 9 and a method for operating a high-pressure injection system according to claim 14.

State of the art

Rotary piston pumps with electric motor are used for various technical applications for pumping a fluid. For example, prefeed pumps serve as fuel pumps for conveying fuel to a high-pressure pump.

In high-pressure injection systems, gerotor pumps with an internal gear and an eccentrically mounted external gear are used as prefeed pumps. In this case, the gerotor pumps have an inflow channel which opens into an inflow working space to introduce the fluid to be conveyed into the inflow working space and has an outflow channel which opens into an outflow working space to discharge the fluid to be conveyed from the outflow working space. The Zuströmarbeitsraum thus represents a suction side of a working space of the gerotor pump and the Abströmarbeitsraum represents a pressure side of the working space.

In high-pressure injection systems with a high-pressure pump and an electric prefeed pump as a gerotor pump, it is known that the fuel is introduced from the prefeed pump into a lubricating space of the high-pressure pump and fed to an inlet channel of the high-pressure pump. The control and / or regulation of the amount of fuel delivered by the high-pressure pump takes place through a metering unit. Moreover, it is known to control the flow rate of the high pressure pump without a metering unit and or regulate. This is an electric prefeed pump whose capacity is controllable and / or regulated. In this case, in turn, the fuel is supplied by the prefeed pump from a fuel tank to the lubricating space and the inlet channel of the high-pressure pump. Such control of the amount of fuel delivered by the high pressure pump without a metering unit is referred to as Feed Pump Control (FPC).

From the DE 36 24 532 C2 For example, there is known a vane or internal gear pump having a plurality of sealed delivery cells whose volume changes from a minimum to a maximum value and back during one revolution. The pump is used in particular for fuel delivery of an internal combustion engine. With axially entering into the feed cells suction and pressure channels, the mouth cross-sections are designed for a promotion without internal compression, but such is created by against axial surfaces of the pump parts applied, check valves forming fixed thrust washers.

From the DE 34 06 349 A1 a displacement machine with at least two gear machines is known, which is associated with its own or common hydraulic circuit, and their common flow is variable by a control means, wherein the control means is arranged in a housing part of the positive displacement machine.

The DE 299 13 367 U1 shows an internal gear pump with at least one internally toothed ring gear and a meshing, externally toothed impeller, with or without sickle, and with an electric drive, which is formed by the ring gear disposed inside a rotor of a brushless electric motor and the rotor adjacent to a stator is, wherein the rotor containing the ring gear is rotatably supported on the outside by a bearing or a sliding bearing, wherein the stator is shielded and sealed relative to the rotor and the interior of the pump characterized in that the located between the stator and rotor bearings or bearings for liquid impermeable and is tightly connected at its two end faces in each case with a cover.

Disclosure of the invention

Advantages of the invention

Inventive rotary piston pump, in particular gear pump, for conveying a fluid, comprising at least one impeller with conveying elements, of which a rotational movement about a rotational axis is executable, a present on the impeller working space, which is divided into an inflow working space and in a Abströmarbeitsraum, one in the Zuströmarbeitsraum opening inflow channel for introducing the fluid to be conveyed into the Zuströmarbeitsraum and a first outflow and second outflow as separate in the Abströmarbeitsraum outflow channels for deriving the fluid to be pumped from the Abströmarbeitsraum, a bypass channel from the first outflow to the inflow channel, preferably a housing, wherein in which an actuator for variable control and / or regulation of the volume flow through the bypass channel is integrated into the bypass channel. In an advantageous manner, the volume flow of fluid conducted through the bypass channel can thereby be changed and adapted to different operating states. As a result, a flexible use of the bypass channel is possible.

Suitably, the rotary piston pump of only one outflow on a bypass channel to the inflow channel.

In particular, variable with the actuator of the controllable by the actuator volume flow of fluid at an identical pressure difference for the fluid on the actuator, in particular the flow cross-sectional area for the fluid through the actuator, changeable, preferably continuously variable. At the actuator of the rotary piston pump or the high-pressure injection system, a pressure difference occurs in the flow direction of the fluid through the bypass channel and in the flow direction of the fluid before the actuator, a higher pressure than after the actuator. With an identical pressure difference on the actuator can be passed through a change of the actuator, a different volume flow of fluid through the actuator and thus through the bypass channel. In particular, the larger the delivery rate and / or the rotational speed of the rotary piston pump, the greater is the pressure difference across the actuator, and vice versa.

In a further embodiment, the flow cross-sectional area can be controlled and / or regulated as a function of at least one parameter with the actuator, and / or the actuator is designed such that the greater the rotational speed of the at least one impeller, the smaller the volume flow that can be conducted by the actuator on fluid at an identical pressure difference for the fluid on the actuator, in particular the smaller the flow cross-sectional area for the fluid through the actuator, and vice versa.

In a supplementary embodiment, the actuator is a valve with a valve spool and a, preferably electrically or pneumatically actuated actuator for moving the valve spool. The electrically or pneumatically actuated actuator is, for example, an electromagnet or a piston operated by compressed air for moving the valve slide.

Preferably, the actuator is a centrifugal valve with a centrifugal shaft.

In one variant, the centrifugal shaft is connected to the impeller, so that the parameter is the speed of the impeller. The centrifugal valve is in particular designed to the effect that the greater the speed of the centrifugal shaft or the rotational speed of the impeller, the smaller is the controllable by the actuator volume flow of fluid at an identical pressure difference for the fluid to the actuator, in particular the smaller the Flow cross-sectional area for the fluid through the actuator.

Suitably, the actuator is a volumetric flow-guided slide valve with a spool and a, in particular integrated in the spool, slide channel and preferably the slide channel forms the second outflow channel. In particular, the slide valve is designed such that the larger the pressure in the second outflow channel, the smaller is the volume flow of fluid through the actuator at an identical pressure difference for the fluid on the actuator, in particular the smaller the flow cross-sectional area for the fluid the actuator, d. H. through the bypass channel.

In a further embodiment, the rotary piston pump is a gear pump, preferably internal gear pump, in particular gerotor pump, and / or the rotary piston pump comprises an electric motor for driving the rotary piston pump, in particular the electric motor is integrated into the rotary piston pump, in particular the gear pump, in particular by a rotor of the electric motor Impeller forms, preferably by permanent magnets are installed in the impeller.

Inventive high-pressure injection system for an internal combustion engine, in particular for a motor vehicle, comprising a high-pressure pump, a high-pressure rail, a prefeed pump for conveying fuel from a fuel tank through a first fuel line to an inlet channel of the high pressure pump and through a second fuel line to a lubrication chamber of the high pressure pump and the Prefetch pump at least one impeller with conveying elements, of which a rotational axis about a rotational movement is executable, an existing on the impeller working space, which is divided into a Zuströmarbeitsraum and in a Abströmarbeitsraum, opening into the Zuströmarbeitsraum inflow channel for introducing the fluid to be conveyed in the Zuströmarbeitsraum comprising a first outflow channel and a second outflow channel as two separate outflow channels opening into the outflow working space and the first outflow channel discharges into the first fuel line and d he second outflow channel opens into the second fuel line, a bypass channel from the first outflow channel and / or the first fuel line to the inflow channel and / or a fuel line from the fuel tank to the inflow channel, wherein in the bypass channel an actuator for variable control and / or regulation of is integrated by the bypass channel conductive volume flow of fuel. With the actuator, the passage of fuel through the bypass channel to different operating conditions of the high-pressure injection system and the internal combustion engine can be adjusted. In particular, in a variable control and / or regulation of the by the Bypass channel conductive volume flow of fluid or fuel at an identical pressure difference across the actuator a different or modified volume flow of fluid or fuel by the actuator or can be conducted.

In particular, with the actuator, the flow cross-sectional area for the fuel by the actuator variable, in particular continuously variable, and / or the actuator, in particular the flow cross-sectional area for the fuel by the actuator is controlled and / or regulated so that the larger of the first Outflow channel guided volume flow of fuel and / or the greater the speed of an impeller, in particular gear, the prefeed pump, the smaller is the controllable by the actuator volumetric flow of fuel with respect to an identical pressure difference on the actuator, in particular the smaller the flow cross-sectional area for the fuel by the actuator, and vice versa and / or the prefeed pump is designed as a rotary piston pump described in this patent application and / or with the high-pressure injection system is described in this patent application process feasible. At a maximum required volume flow of fuel for the high-pressure pump and the inlet channel of the high-pressure pump, the actuator is completely closed, so that thereby the entire funded by the first outflow volume flow of fuel of the high-pressure pump is available. As a result, during operation of the prefeed pump for conveying the maximum volume flow of fuel for the high-pressure pump, only that rotational speed of the prefeed pump is required in order to convey this volume flow through the first outflow channel. At this speed of the prefeed pump for conveying the maximum volume flow of fuel through the first outflow channel to the high-pressure pump is also a sufficient volume flow at the second outflow channel for the lubricating space available. If the internal combustion engine or the high-pressure pump requires less than the maximum volume flow, the speed of the prefeed pump can be reduced and, at the same time, the actuator is opened so that fuel also flows through the bypass channel. An opening of the actuator is preferably required so that the feed pump is operated in a speed range in which a sufficient volume flow of fuel through the second outflow channel and thereby the lubricating space is passed and at the same time a small volume flow of fuel is conveyed to the high pressure pump, as by the bypass channel guided volume flow of fuel is not promoted to the high-pressure pump.

In a further embodiment, the actuator is a valve with a valve spool and a, preferably electrically or pneumatically actuated actuator for moving the valve spool.

In a supplementary variant, the actuator is a centrifugal slide with a centrifugal shaft and preferably the centrifugal shaft is connected to the impeller of the prefeed pump, so that the controllable through the bypass passage volume flow of fuel in dependence on the speed of the impeller of the prefeed pump is controllable and / or regulated.

In a further variant, the actuator is a volumetric flow-guided slide valve with a slide piston, an elastic valve element, in particular a valve spring, and a, in particular in the spool integrated slide channel and preferably the slide channel forms the second outflow channel and / or the second fuel line.

Method according to the invention for operating a high-pressure injection system, in particular a high-pressure injection system described in this patent application, comprising the steps of: conveying fuel with a prefeed pump from a fuel tank through an inflow working space, through an outflow working space and through a first outflow channel from the outflow working space and through a first fuel line to one Inlet opening of a high-pressure pump, conveying fuel with the prefeed pump from the fuel tank through the Zuströmarbeitsraum, through the Abströmarbeitsraum and through a second outflow channel from the Abströmarbeitsraum and through a second fuel line to a lubrication chamber of the high pressure pump, passing fuel through a bypass passage from the first outflow channel and / or the first fuel line to the inflow channel and / or to a fuel line from the fuel tank in the Zuströmarbeitsraum, wherein with a Stell organ of the guided through the bypass channel volume flow of fuel is controlled and / or regulated.

Suitably, the fuel is separated from the Abströmarbeitsraum separated by the first and second discharge channel.

In a further embodiment, the volume flow is controlled and / or regulated by changing the volume flow, in particular the flow cross-sectional area for the fuel, on the actuator in dependence on at least one parameter, in particular the at least one parameter is the rotational speed of an impeller of the prefeed pump and / or the volume flow of fuel flowing through the first outflow channel and / or or the volumetric flow of fuel flowing through the second outflow channel and / or the rotational speed of the internal combustion engine and / or the torque requested by the internal combustion engine and / or the required and / or actual volume flow of fuel and / or the fuel through an inlet channel of the high-pressure pump a gear pump, in particular a gerotor pump, is conveyed as a prefeed pump and / or the greater the rotational speed of the impeller of the prefeed pump and / or the greater the volume flow of fuel flowing through the first outflow channel, the smaller the flow cross-sectional area for the fuel on the actuator and vice versa, In particular, the rotational speed of the impeller of the prefeed pump and / or the volume flow of fuel flowing through the first outflow channel is indirectly proportional to the volume flow of fuel passed through the actuator with respect to an identical pressure difference of the fuel at the Stellorg on, in particular indirectly proportional to the flow cross-sectional area for the fuel to the actuator. In one embodiment of the actuator as a valve with an electrically operated valve slide, the valve can be controlled and / or regulated as a function of at least one parameter. In an embodiment of the actuator as a valve with the valve slide, for example, the volume flow of fuel flowing through the first and second outflow ducts is detected and, furthermore, the volume flow of fuel requested by the inlet duct of the high-pressure pump and / or actual. At a maximum volume flow of fuel through the inlet channel of the high-pressure pump, the actuator is completely closed, so that the entire flowing through the first outflow volume flow of fuel of the high-pressure pump is available. If a lower than the maximum volume flow of fuel is required at the inlet channel of the high pressure pump, the actuator as valve with the valve spool remains fully closed until the required volume flow of fuel for the inlet channel at which the minimum required due to the reduced speed of the feed pump Volume flow of fuel at the second outflow channel for the lubricant space occurs. In a further decrease in the required or actual volume flow of the fuel at the inlet channel of the high-pressure pump, the speed of the prefeed pump is maintained at that speed range, which is required to provide the minimum required volume flow of fuel for the lubricating space and a further decrease in the required volume flow of fuel for the high-pressure pump, the actuator is further opened as a valve with the valve spool, so that on the one hand by the inlet channel for the high-pressure pump pumped volume flow of fuel continues to fall and still due to the constant speed of the feed pump for the lubricating space of the high-pressure pump minimum volume flow of fuel is available for lubrication and cooling of the lubrication space. As a result, the required energy for the electric prefeed pump can be minimized or optimized in an advantageous manner. Such control and / or regulation of the actuator is preferably carried out by an electronic control system as engine electronics for the internal combustion engine, so that other parameters can be taken into account, for. B. a different minimum flow of fuel passed through the lubricant space, since at a higher speed and / or temperature of the engine, a larger minimum (minimum required) volume flow of fuel through the lubricant space is required as at a low speed and / or temperature of the engine ,

In particular, in each position of the at least one impeller with the conveying elements substantially no fluid-conducting connection between the two outflow channels through the Abströmarbeitsraum. There is thus essentially no fluid-conducting connection between the two outflow channels through the outflow working space. This is made available in particular by a geometry or a distance of the two outflow channels, so that at least one delivery element of the impeller constantly seals within the outflow working space an outflow channel from the other outflow channel. Pressure surges on one outflow channel do not reach the other outflow channel.

In a further embodiment, the conveying elements are teeth of a toothed wheel.

Preferably, the internal gear pump comprises an internal gear having an internal gear and an external gear having an external gear, wherein the teeth of the internal gear mesh with the teeth of the external gear and the working space is formed between the internal gear and the external gear.

In an additional embodiment, the internal gear is mounted eccentrically to the external gear.

In one variant, the amount, in particular the volume, of the fluid conveyed through the two outflow passages varies per revolution of the at least one impeller, in particular the amount of fluid conducted through the first outflow passage is greater than the quantity of fluid passed through the second outflow passage. From the rotary piston pump thus different volume flows at the first outflow channel and at the second outflow of the two separate outflow channels are provided. The rotary piston pump can thereby provide two separate volume flows with a different volume flow as two different rotary piston pumps with a different flow rate available.

In particular, the delivery rate of the rotary piston pump, preferably with an integrated electric motor, can be controlled and / or regulated, in particular by the power and / or rotational speed of the electric motor being controllable and / or controllable.

In a supplementary variant, there is essentially no fluid-conducting connection between the first fuel line and the second fuel line. Pressure surges in the lubricating space thereby do not reach the inlet valve of the high-pressure pump and even in the case of pressure surges within the lubricating space due to the oscillating movement of the piston of the high-pressure pump, the function of the high-pressure pump at the inlet valve of the high-pressure pump is not restricted. The rotary piston pump is designed such that in any position of the impeller of the rotary piston pump there is substantially no fluid-conducting connection between the two outflow channels through the Abströmarbeitsraum the rotary piston pump. In particular, the gears of the gerotor pump constantly separate the Abströmarbeitsraum at the first outflow from the Abströmarbeitsraum at the second outflow from.

The bypass channel connects the first outflow channel or the first fuel line with the inflow channel. In certain operating conditions of the internal combustion engine in the motor vehicle, for. As in a downhill of the motor vehicle, it is necessary that no fuel is delivered through the first fuel line to the inlet valve of the high pressure pump, because in a Begabfahrt to the engine no fuel is required and still lubrication of the high-pressure pump is required due to the movement of moving parts in the high pressure pump. By means of the bypass channel, the fuel delivered through the first outflow channel can again be supplied to the inflow channel, so that no fuel reaches the inlet valve of the high-pressure pump and nevertheless fuel is passed through the lubricant space through the second outflow channel and by means of the actuator, the fuel can pass through the bypass channel Volumetric flow of fuel can be controlled and / or regulated.

In a further embodiment, the prefeed pump is a prefeed pump with an electric motor, so that the prefeed pump is driven by the electric motor and, in particular, the delivery rate of the prefeed pump can be controlled and / or regulated.

Suitably, the rotary piston pump is a rotary vane pump, a rotary lobe pump or a centrifugal pump.

In a supplementary variant, the at least one impeller represents the rotary piston of the rotary piston pump.

In a further embodiment, the rotary piston pump with electric motor is enclosed by the housing. The pump with electric motor thus has one or more parts housing and within the housing, the rotary piston pump is arranged with electric motor.

Suitably, the rotary piston pump with, preferably integrated, electric motor comprises a, preferably electronic, control unit for controlling the energization of the electromagnets and / or the electric motor is a brushless or electronically commutated electric motor.

Suitably consists of the housing of the rotary piston pump and / or the housing of the high pressure pump and / or the inner and / or outer gear at least partially, in particular completely, made of metal, for. As steel or aluminum.

Brief description of the drawings

Hereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings. It shows:

1 a cross section of a high-pressure pump for conveying a fluid,

2 a section AA according to 1 a roller with roller shoe and a drive shaft,

3 a highly schematic view of a high-pressure injection system,

4 a greatly simplified cross-section of the high-pressure pump with a prefeed pump,

5 a perspective view of a prefeed pump without housing and a stator,

6 an exploded view of the feed pump according to 5 with housing,

7 a cross-section of an inner and outer gear of the feed pump according to 5 .

8th a diagram of the delivery Q ₁ and Q ₂ at the first and second outflow channel in Depending on the speed n of the external gear of the feed pump according to 5 .

9 a cross section of an actuator in a first embodiment in an open position,

10 a cross section of the actuator according to 9 in a closed position,

11 a cross section of the actuator in a second embodiment in an open position,

12 a cross section of the actuator according to 11 in a closed position,

13 a cross section of the actuator in a third embodiment in an open position,

14 a cross section of the actuator according to 13 in a closed position and

15 a view of a motor vehicle.

Embodiments of the invention

In 1 is a cross section of a high pressure pump 1 shown for conveying fuel. The high pressure pump 1 serves to fuel, z. As gasoline or diesel, to an internal combustion engine 39 for a motor vehicle 38 ( 15 ) under high pressure. The from the high pressure pump 1 producible pressure is for example in a range between 1000 and 3000 bar.

The high pressure pump 1 has a drive shaft 2 with two cams 3 on that around an axis of rotation 26 performs a rotational movement. The rotation axis 26 lies in the drawing plane of 1 and is perpendicular to the plane of 2 , A piston 5 is in a cylinder 6 stored by a housing 8th the high pressure pump 1 is formed. A high pressure workroom 29 is from the cylinder 6 as a piston guide 7 , the housing 8th and the piston 5 limited. In the high pressure workroom 29 opens an inlet channel 22 with an inlet valve 19 and an exhaust duct 24 with an exhaust valve 20 , Through the inlet channel 22 with the inlet opening 21 the fuel flows into the high-pressure working space 29 in and through the outlet channel 24 with an outlet opening 23 the fuel flows under high pressure from the high-pressure working space 29 out again. The inlet valve 19 , z. As a check valve, is designed such that only fuel in the high pressure working space 29 can flow in and the exhaust valve 20 , z. B. a check valve, is designed such that only fuel from the high-pressure working space 29 can flow out. The volume of the high pressure workspace 29 is due to an oscillating stroke movement of the piston 5 changed. The piston 5 rests indirectly on the drive shaft 2 from. At the end of the piston 5 or pump piston 5 is a roller shoe 9 with a roller 10 attached. The roller 10 can perform a rotational movement, the axis of rotation 25 in the drawing plane according to 1 lies and perpendicular to the plane of 2 stands. The drive shaft 2 with the at least one cam 3 has a wave rolling surface 4 and the roller 10 a roller rolling surface 11 on.

The roller tread 11 the roller 10 rolls on the wave rolling surface 4 as a contact surface 12 the drive shaft 2 with the two cams 3 from. The roller shoe 9 is in one of the housing 8th formed roller shoe storage stored as a plain bearing. A feather 27 or spiral spring 27 as an elastic element 28 between the case 8th and the roller shoe 9 is clamped, brings on the roller shoe 9 a compressive force on, leaving the roller rolling surface 11 the roller 10 in constant contact with the shaft rolling surface 4 the drive shaft 2 stands. The roller shoe 9 and the piston 5 thus jointly carry out an oscillating lifting movement. The roller 10 is with a sliding bearing 13 in the roller shoe 9 stored.

In 3 is a highly schematic representation of a high-pressure injection system 36 for the motor vehicle 38 Shown with a high pressure rail 30 or a fuel rail 31 , From the high-pressure rail 30 or a fuel rail 31 the fuel is injected into the combustion chambers of the internal combustion engine by means of injectors (not shown) 39 injected. An electric feed pump 35 Promotes fuel from a fuel tank 32 through a first fuel line 33a to the inlet duct 22 and through a second fuel line 33b to a lubrication room 40 ( 4 ) of the high pressure pump 1 , A bypass channel 37 connects the first fuel line 33a with the fuel line 33 from the fuel tank 32 to the pre-feed pump 35 , The high pressure pump 1 is doing from the drive shaft 2 driven and the drive shaft 2 is a wave, z. B. a crankshaft or camshaft, the engine 39 , The delivery rate of the electric prefeed pump 35 is controllable and / or controllable, so that thereby to the inlet duct 22 subsidized amount of fuel can be controlled and / or regulated. The high pressure rail 30 serves to transport the fuel into the combustion chambers of the internal combustion engine 39 inject. The from the high pressure pump 1 Unnecessary fuel is through a fuel return line 34 back in the fuel tank 32 returned.

4 shows a part of the high-pressure injection system 36 , Inside the case 8th of the high pressure pump 1 is the lubrication room 40 educated. In the lubrication room 40 are the drive shaft 2 , the roller 10 , the roller shoe 9 (not in 4 ) and partially the piston 5 arranged. Through the through the lubricating space 40 Guided fuel will be these components 2 . 5 . 9 and 10 lubricated by the fuel. The through the second fuel line 33b in the lubrication room 40 Fuel introduced is through the fuel return line 34 from the lubricating space 40 discharged from the fuel tank 32 fed again ( 4 ). In 4 is that in 3 illustrated high-pressure injection system 36 in more detail without the high pressure rail 30 and without the internal combustion engine 39 shown. The from the pre-feed pump 35 from the fuel tank 32 sucked fuel is from the pre-feed pump 35 with a prefeed pressure, z. B. 4 bar, through the first fuel line 33a the inlet channel 22 the high pressure pump 1 fed. Furthermore, that of the prefeed pump 35 subsidized fuel during operation of the internal combustion engine 39 through the second fuel line 33b the lubricating space 40 supplied for lubrication, z. B. the drive shaft 2 , the roller 10 and the piston 5 , After flowing through the fuel through the lubricating space 40 the fuel is returned through the fuel return line 34 the fuel tank 32 fed. This allows these components 2 . 5 . 9 and 10 lubricated as well as cooled. The pre-feed pump 35 promotes in addition to the flow rate for the high-pressure pump 1 Fuel also an additional amount of fuel or volume flow for lubrication of the high-pressure pump 1 , ie the fuel passing through the lubricating space 40 flows.

The electric prefeed pump 35 has an electric motor 17 and a rotary piston pump 16 namely a gear pump 14 ie an internal gear pump 15 or gerotor pump 15 on ( 5 and 6 ). Here is the electric motor 17 the gerotor pump 15 in the gerotor pump 15 integrated. The high pressure pump 1 promotes fuel under high pressure, for example, a pressure of 1000, 3000 or 4000 bar, through a high pressure fuel line to a high pressure rail 31 , From the high-pressure rail 31 the fuel is under high pressure by one injector each a combustion chamber (not shown) of the internal combustion engine 39 fed. The electric motor 17 ( 5 and 6 ) of the electrical feed pump 35 is operated with three-phase current or alternating current and is controllable in power and / or regulated. The three-phase current or alternating current for the electric motor 17 is from a power electronics, not shown, from a DC voltage network of a vehicle electrical system of a motor vehicle 38 made available. The electric prefeed pump 35 is thus an electronically co-fed prefeed pump 35 ,

The electric prefeed pump 35 or gerotor pump 15 has a housing 42 with a housing pot 44 and a housing cover 43 on ( 6 ). Inside the case 42 the pre-feed pump 35 are the gerotor pump 15 as internal gear pump 15 or gear pump 14 and the electric motor 17 arranged. The housing pot 44 is with a recess 72 Mistake. The electric motor 17 has a stator 47 with windings 48 as electromagnets 49 and a soft iron core 70 as a soft magnetic core 68 that as a laminated core 69 is trained. Inside the stator 47 is the gerotor pump 15 as internal gear pump 15 with an internal gear 56 with an internal toothed ring 57 and an external gear 58 with an external tooth ring 59 positioned. The internal and external gear 56 . 58 makes a gear 54 and an impeller 52 and the inner and outer teeth ring 57 . 59 have teeth 55 as conveying elements 53 on. Between the inner and outer gear 56 . 58 a working room is formed 62 out. In the external gear 58 are permanent magnets 51 fitted so that the external gear 58 also a rotor 50 of the electric motor 17 forms. The electric motor 17 is thus in the gerotor pump 15 integrated or vice versa. The electromagnets 49 of the stator 47 are alternately energized, so that due to the contact with the electromagnet 49 resulting magnetic field of the rotor 50 or the external gear 58 in a rotational movement about a rotation axis 61 is offset.

The housing cover 43 serves as a warehouse 45 or thrust bearing 45 or slide bearing 45 for the internal or external gear 56 . 58 , In addition, the housing pot 44 and the housing cover 43 three holes each 71 on, in which screws, not shown, for screwing together the housing pot 44 and the housing cover 43 are positioned, with a seal, not shown, the housing pot 44 and the housing cover 43 lie fluid-tight on each other. The recess 72 on the housing pot 44 serves to cut at the recess 72 electrical contact elements or lines to the electromagnet 49 respectively.

In 7 is the cross section of the internal gear 56 and the external gear 58 the gerotor pump 15 shown. Between the internal gear 56 and the external gear 58 the working space is formed 62 the internal gear pump 15 out. Will the inner and outer gear 56 . 58 rotated counterclockwise, with the inner and outer gears 56 . 58 Are mounted eccentrically to each other, forms on the inner and outer gear 56 . 58 ie between the inner and outer gears 56 . 58 , the workspace 62 out. At an angle range 73 of 180 ° forms a Zuströmarbeitsraum 63 from, at which the working space 62 increases and thereby a suction side of the internal gear pump 15 is present. At an angle range 74 of working space 62 arises the Abströmarbeitsraum 64 in which the working space 62 reduced and thereby a pressure side of the internal gear pump 15 arises. Into the inflow workspace 63 an inflow channel opens 65 , which on the housing 8th the internal gear pump 15 is trained. The inflow channel 65 has an angular range 18 less than 180 °. In the downstream workspace 64 opens a first outflow channel 66 and a second outflow channel 67 each with an angular range 46 , The inflow channel 65 and the first and second outflow channels 66 . 67 are in 7 each shown in dashed lines. From the Abströmarbeitsraum 64 can thus by two hydraulically separated outflow channels 66 . 67 the fuel hydraulically separated from the Abströmarbeitsraum 64 be derived. The sealing distance or the angular range 75 between the two outflow channels 66 . 67 ie the distance between the two outflow channels 66 . 67 , is chosen to the effect that on the one hand to no complete closing of the pumping rooms on the teeth 55 between the inner and outer gears 56 . 58 comes and thus to a blockage of gerotor pump 15 and on the other hand, no leakage between the two outflow channels 66 . 67 is present, so that in every position of the internal and external gear 56 . 58 no fluid-conducting connection between the two outflow channels 66 . 67 consists. There is thus essentially no fluid-conducting connection, in particular of the second outflow channel 67 to the first outflow channel 66 ,

The through the first outflow channel 66 Guided fuel is through the first fuel line 33a an inlet valve 19 the high pressure pump 1 fed and the through the second outflow channel 67 Guided fuel is passing through the second fuel line 33b the lubricating space 40 supplied ( 4 ). Due to the lack of fluid-conducting connection from the second outflow channel 67 in the first outflow channel 66 can thereby pressure fluctuations in the lubricating space 40 , which due to the oscillating movements of the piston 5 in the lubrication room 40 Do not occur through the gerotor pump 15 and the first fuel line 33a to the inlet valve 19 the high pressure pump 1 procreate. Even with strong pressure fluctuations and pressure surges in the lubricating space 40 is thereby a proper function of the inlet valve 19 guaranteed as a check valve and thus also a proper function of the high-pressure pump 1 , The delivery rate of the gerotor pump 15 is controllable and / or controllable, since these are controllable by a power electric motor 17 is driven. A complex and expensive metering unit is not required and only by controlling and / or regulating the delivery rate of the gerotor pump 15 can the capacity of the high pressure pump 1 controlled and / or regulated.

The first outflow channel 66 or the first fuel output 33a is through the bypass channel 37 fluid-conducting with the fuel line 33 from the fuel tank 32 to the gerotor pump 15 or to the inflow channel 65 the gerotor pump 15 connected. In certain operating conditions of the internal combustion engine 39 of the motor vehicle 38 It may be necessary for the gerotor pump 15 no fuel to the high pressure pump 1 but fuel through the lubrication space 40 to lead is. This is done by an actuator 41 at the bypass channel 37 the bypass channel 37 open and thereby comes to a or at a certain speed _n'B in a partially open actuator 41 or capacity of the gerotor pump 15 through the first outflow channel 66 delivered volume flow Q ₁ of fuel through the bypass channel 37 back to the fuel line 33 or the inflow channel 65 , thereby making the gerotor pump 15 with respect to the first outflow channel 66 shorted. For a fully open actuator 41 reaches up to one or at a certain speed n'' _B at the fully open actuator 41 or capacity of the gerotor pump 15 through the first outflow channel 66 delivered volume flow Q ₁ of fuel through the bypass channel 37 back to the fuel line 33 or the inflow channel 65 , Through the second outflow channel 67 is a certain flow or a certain volume flow Q ₂ of fuel through the lubricating space 40 promoted. Such an operating state is, for example, at a downhill of the motor vehicle 38 given. In 8th is in a diagram on the abscissa, the speed n of the inner or outer gear 56 . 58 and plotted on the ordinate of the volume flow Q. The ratio between the volume flow Q ₁ to the volume flow Q ₂ results from the length ratios of the first and second outflow channel 66 . 67 , In 8th is the one through the inlet opening 21 the high pressure pump 1 directed flow Q _'1 in a partially open bypass channel 37 dashed lines shown as a straight line and a fully open bypass channel 37 is the one through the inlet opening 21 the high pressure pump 1 directed volumetric flow Q'' ₁ also shown in dashed lines as a straight line. The solid line for Q ₁ represents the volume flow through the first outflow channel 66 and the solid line for Q ₂ represents the volume flow through the second outflow channel 67 or the lubricating space 40 . Up to a rotational speed N _B or _B n'' the inner or outer gear 56 . 58 is at a partially or fully open actuator 41 no fuel as volume flow Q ₁ 'and Q ₁ ''to the inlet port 21 promoted, because the entire through the first outflow 66 pumped fuel through the bypass channel 37 again the inflow channel 65 can be supplied, however, through the second outflow channel 67 Fuel through the lubricating space 40 , Only at a crossing of the speed _n'B or _B is n'' even with a partially or fully open actuator 41 Fuel to the inlet opening 21 the high pressure pump 1 promoted. Opening the actuator 41 thus causes a passage of fuel through the bypass passage 37 as volume flow Q _B , thereby passing through the inlet port 21 directed flow Q ₁ 'and Q _1'' compared to the flow rate Q is reduced _1, ie, Q _1' = Q ₁ - Q _B 'for a partially open actuator 41 or Q _{1 '} ' = Q ₁ - Q _B '' and for a fully open actuator 41 , please refer 8th ,

In 8th is Q _'B through the bypass passage 37 directed volume flow of fuel at a partially open actuator 41 represented and with Q'' _B through the bypass channel 37 Guided volume flow of fuel at a fully open actuator 41 shown. At the maximum speed n _{max of} the internal or external gear 56 . 58 occurs at the first outflow channel 66 and the inlet opening 21 in a fully closed actuator 41 the volume flow max Q ₁ on. Requires the high pressure pump 1 , z. B. due to a maximum torque request by the driver of the motor vehicle 38 , at the inlet opening 21 or the first fuel line 33a the maximum volume flow of fuel would be at a partially or fully open actuator 41 a part of the through the first outflow channel 66 subsidized fuel through the bypass channel 37 be derived and not the high pressure pump 1 are available, ie part of the pre-feed pump 35 consumed electrical energy would be unnecessarily consumed. For this reason, at the maximum demand of the volume flow of fuel for the high-pressure pump 1 the actuator 41 completely closed, leaving the entire through the first outflow 66 delivered volume flow Q ₁ to fuel the high-pressure pump 1 is available. This is due to the prefeed pump 35 for the maximum volume flow of fuel for the high-pressure pump 1 a smaller volume flow Q ₁ at the first outflow channel 66 and a smaller maximum speed n _max required than an open actuator 41 , so that thereby electrical energy for the operation of the feed pump 35 can be saved. At the maximum volume flow of fuel for the high-pressure pump 1 and the fully closed actuator 41 becomes the prefeed pump 35 operated at the maximum speed n _max , so that also at the second outflow channel 67 the maximum volume flow Q ₂ occurs and for sufficient cooling and lubrication of the lubricating space 40 provides.

In 9 and 10 is a first embodiment of the actuator 41 as a valve 76 shown. The valve 76 has a movable valve spool mounted on a cylinder 77 on and on the valve spool 77 brings in as a valve spring 81 trained elastic valve element 80 a force to that of the valve spring 81 the movable valve spool 77 in a full closed position according to 10 is moved. To open the valve spool 77 becomes the electromagnet 79 trained actuator 78 energized, so that opposite to the valve spring 81 on the valve spool 77 applied pressure force of the valve slide 77 from the in 10 represented full closed position in the 9 shown full open position is moved. This allows the Flow cross-sectional area for the fuel through the bypass channel 37 to be changed. In this case, an average flow cross-sectional area is considered as the flow cross-sectional area, since the longer the energization times of the electromagnet 70 are, the larger the flow cross-sectional area or the average flow cross-sectional area for the fuel through the bypass channel 37 , The valve spool 77 Thus, only between the fully closed position according to 10 and the fully open position according to 9 to be moved. The electromagnet 79 is supplied with a sawtooth voltage.

In 11 and 12 is a second embodiment of the centrifugal slide 88 trained actuator 41 shown. The centrifugal valve 88 has a centrifugal shaft 82 on which with the internal or external gear 56 . 58 the pre-feed pump 35 connected is. rotating arms 84 are by means of joints with the centrifugal shaft 82 and several rotational masses 83 connected. Furthermore, the rotational masses 83 with rotation arms 84 and joints with the valve spool 77 connected. This brings the valve spring 81 an axial force to the valve spool 77 on that this in the in 11 illustrated opening position is located. The valve spool 77 has a pertinent geometry that, in a movement from the open position in 11 in the closed position according to 12 to the top of the bypass channel 37 closed is. With an increase in the speed of the internal or external gear 56 . 58 the pre-feed pump 35 also increases the speed of the centrifugal shaft 82 , so that thereby on the rotational masses 83 indicating the rotational movement of the centrifugal shaft 82 with execute, a correspondingly larger centripetal acceleration acts and thus the valve spool 77 from the in 11 illustrated opening position in the in 12 shown closed position is moved. In 12 points the valve spool 77 a full closed position, so that no fuel through the bypass channel 37 can flow. When moving the valve spool 77 from the in 11 illustrated complete open position to the in 12 shown full closed position is in the intermediate position of the valve spool 77 the flow cross-sectional area for the fuel through the bypass passage 37 infinitely reduced. The greater the speed of the centrifugal shaft 82 is, the smaller is thereby the fuel available flow cross-sectional area at the bypass channel 37 and vice versa.

In 13 and 14 is a third embodiment of the actuator 41 as a slide valve 85 shown. The slide valve 85 has a spool 86 on which is movably mounted on a cylinder. Here is the spool 86 with an axial bore as a slide channel 87 provided so that through the spool 86 in the slide channel 87 Fuel can flow. The slide channel forms 87 the second fuel line 33b so that through the slider channel 87 directed volumetric flow of fuel the volume flow Q ₂ at the second outflow channel 67 or through the lubricating space 40 passed volume flow corresponds to fuel. Through the bypass channel 37 the volume flow Q _{B is passed} . Furthermore acts on the spool 86 the valve spring 81 , The larger the through the slide channel 87 Guided volume flow Q ₂ to fuel, the greater the back pressure on the left of the spool 86 , This acts on the spool 86 at the in 13 and 14 illustrated left axial end, a greater back pressure, the larger the through the slide channel 87 directed volume flow Q _{2 is} to fuel. With an increase in this back pressure thereby the spool 86 opposite to the valve spring 81 on the spool 86 applied force from the in 13 illustrated opening position in the in 14 shown closed position moves. When the back pressure drops to the left of the axial end of the spool 86 on the second fuel line 33b can the spool 86 from the in 14 shown closed position of the valve spring 81 back in the 13 shown opening position to be moved. The larger the through the slide channel 87 or the second fuel line 83 Guided volume flow Q ₂ to fuel, the smaller is that of the slide valve 85 provided flow cross-sectional area for the fuel through the bypass passage 37 and vice versa.

Overall, considered with the high-pressure injection system according to the invention 36 significant benefits. At a high or a maximum capacity of the pre-feed pump 1 to fuel to the high pressure pump 1 is due to the high speed of the feed pump 35 a sufficient volume flow of fuel Q ₂ through the lubricant space 40 passed and through the second outflow channel 67 directed. For this reason, it is in an operating state of the prefeed pump 35 at a high or maximum speed range of the pre-feed pump 35 not desired, fuel through the bypass channel 37 derive. For this reason, with the actuator 41 at a high or maximum speed range of the pre-feed pump 35 the bypass channel 35 at least partially closed so that thereby the whole or the substantially entire through the first outflow channel 66 directed volumetric flow of fuel of the high-pressure pump 1 is available. As a result, in this operating state, the energy consumption of the electric prefeed pump 35 be reduced. Even at a low volume flow request Q ₁ 'of fuel to the high pressure pump 1 a sufficient volume flow of fuel Q ₂ through the second outflow channel 67 to be able to guide, becomes the actuator 41 opened, so that on the one hand to the high pressure pump 1 a small volume flow of fuel is conveyed, as part of the flow through the first outflow 66 funded volume flow Q ₁ through the bypass channel 37 is derived as a volume flow Q _B and on the other hand, a sufficient volume flow Q ₂ of fuel through the second outflow channel 67 can be promoted due to the speed n of the feed pump 35 for cooling and lubrication of the lubricating space 40 , At a constant volume flow Q ₂ at the second outflow channel 67 and the lubrication room 40 and a constant speed n of the prefeed pump 35 causes an opening of the actuator 41 a lowering of the to the high pressure pump 1 transported volume flow Q ₁ or Q `` _`1 of the fuel and increasing the through the bypass channel 37 directed volume flow Q _{B of} the fuel.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 3624532 C2 [0005]
• DE 3406349 A1 [0006]
• DE 29913367 U1 [0007]

Claims (15)

Rotary piston pump ( 16 ), in particular gear pump ( 14 ), for conveying a fluid, comprising - at least one impeller ( 52 ) with conveying elements ( 53 ) of which about a rotation axis ( 61 ) a rotational movement is executable, - one on the impeller ( 52 ) existing work space ( 62 ) entering an inflow workspace ( 63 ) and in a downstream working space ( 64 ), - one in the Zuströmarbeitsraum ( 63 ) inflowing inflow channel ( 65 ) for introducing the fluid to be conveyed into the inflow work space ( 63 ) and a first outflow channel ( 66 ) and second outflow channel ( 67 ) as separated into the effluent working space ( 64 ) outflow channels ( 66 . 67 ) for diverting the fluid to be delivered from the Abströmarbeitsraum ( 64 ), - a bypass channel ( 37 ) from the first outflow channel ( 66 ) to the inflow channel ( 65 ), Preferably a housing ( 42 ), whereby, in the bypass channel ( 37 ) an actuator ( 41 ) for the variable control and / or regulation of the by the bypass channel ( 37 ) is integrated flow volume of fluid. Rotary piston pump according to claim 1, characterized in that with the actuator ( 41 ) by the actuator ( 41 ) conductive volume flow of fluid at an identical pressure difference for the fluid on the actuator ( 41 ), in particular the flow cross-sectional area for the fluid through the actuator ( 41 ), changeable, preferably continuously variable, is. Rotary piston pump according to claim 2, characterized in that with the actuator ( 41 ) the flow cross-sectional area can be controlled and / or regulated as a function of at least one parameter and / or the actuator ( 41 ) is designed such that the greater the rotational speed of the at least one impeller ( 52 ) is, the smaller the by the actuator ( 41 ) conductive volume flow of fluid at an identical pressure difference for the fluid on the actuator ( 41 ), in particular the smaller the flow cross-sectional area for the fluid through the actuator ( 41 ), and vice versa. Rotary piston pump according to one or more of the preceding claims, characterized in that the actuator ( 41 ) a valve ( 76 ) with a valve slide ( 77 ) and a, preferably electrically or pneumatically actuated actuator ( 78 ), for moving the valve spool ( 77 ). Rotary piston pump according to one or more of claims 1 to 3, characterized in that the actuator ( 41 ) a centrifugal slide valve ( 88 ) with a centrifugal shaft ( 82 ). Rotary piston pump according to claim 5, characterized in that the centrifugal force wave ( 82 ) with the impeller ( 52 ), so that the parameter is the speed of the impeller ( 52 ). Rotary piston pump according to one or more of claims 1 to 3, characterized in that the actuator ( 41 ) a flow-controlled slide valve ( 85 ) is with a spool ( 86 ) and one, in particular in the spool ( 86 ) integrated, slide channel ( 87 ) and preferably the slide channel ( 87 ) the second outflow channel ( 67 ). Rotary piston pump according to one or more of the preceding claims, characterized in that the rotary piston pump ( 16 ) a gear pump ( 14 ), preferably internal gear pump ( 15 ), in particular gerotor pump ( 15 ), and / or the rotary piston pump ( 16 ) an electric motor ( 17 ) for driving the rotary piston pump ( 16 ), in particular the electric motor ( 17 ) in the rotary piston pump ( 16 ), in particular the gear pump ( 14 ), in particular by a rotor ( 50 ) of the electric motor ( 17 ) an impeller ( 52 ), preferably by permanent magnets ( 51 ) in the impeller ( 52 ) are installed. High-pressure injection system ( 36 ) for an internal combustion engine ( 39 ), in particular for a motor vehicle ( 38 ), comprising - a high-pressure pump ( 1 ), - a high-pressure rail ( 30 ), - a prefeed pump ( 35 ) for conveying fuel from a fuel tank ( 32 ) through a first fuel line ( 33a ) to an inlet channel ( 22 ) of the high-pressure pump ( 1 ) and a second fuel line ( 33b ) to a lubricating space ( 40 ) of the high-pressure pump ( 1 ) and the pre-feed pump ( 35 ) at least one impeller ( 52 ) with conveying elements ( 53 ) of which about a rotation axis ( 61 ) a rotational movement is executable, one on the impeller ( 52 ) existing work space ( 62 ) entering an inflow workspace ( 63 ) and in a downstream working space ( 64 ), one in the Zuströmarbeitsraum ( 63 ) inflowing inflow channel ( 65 ) for introducing the fluid to be conveyed into the inflow work space ( 63 ), a first outflow channel ( 66 ) and a second outflow channel ( 67 ) as two separate in the Abströmarbeitsraum ( 64 ) outflow channels ( 66 . 67 ) and the first outflow channel ( 66 ) into the first fuel line ( 33a ) and the second outflow channel ( 67 ) into the second fuel line ( 33b ), A bypass channel ( 37 ) from the first outflow channel ( 66 ) and / or the first fuel line ( 33a ) to the inflow channel ( 65 ) and / or a fuel line ( 33 ) from the fuel tank ( 32 ) to the inflow channel 65 ), whereby, in the bypass channel ( 37 ) an actuator ( 41 ) for the variable control and / or regulation of the by the bypass channel ( 37 ) Flowable volume of fuel is integrated. High-pressure injection system according to claim 9, characterized in that with the actuator ( 41 ) the flow cross-sectional area for the fuel by the actuator ( 41 ) changeable, in particular continuously variable, is and / or the actuator ( 41 ), in particular the flow cross-sectional area for the fuel by the actuator ( 41 ) is controlled and / or regulated in such a way that the larger the flow through the first outflow channel ( 66 ) guided volume flow of fuel and / or the greater the speed of an impeller ( 52 ), in particular gear ( 54 ), the prefeed pump ( 35 ) is, the smaller the by the actuator ( 41 ) conductive volume flow of fuel with respect to an identical pressure difference at the actuator ( 41 ), in particular the smaller the flow cross-sectional area for the fuel by the actuator ( 41 ), and vice versa and / or the prefeed pump ( 35 ) as a rotary piston pump ( 16 ) according to one or more of claims 1 to 8 and / or with the high-pressure injection system ( 36 ) a method according to claim 14 or 15 is executable. High-pressure injection system according to claim 9 or 10, characterized in that the actuator ( 41 ) a valve ( 76 ) with a valve slide ( 77 ) and a, preferably electrically or pneumatically actuated actuator ( 78 ), for moving the valve spool ( 77 ). High-pressure injection system according to claim 9 or 10, characterized in that the actuator ( 41 ) a centrifugal slide valve ( 88 ) with a centrifugal shaft ( 82 ) and preferably the centrifugal shaft ( 82 ) with the impeller ( 52 ) of the feed pump ( 35 ), so that through the bypass channel ( 37 ) conductive volume flow of fuel as a function of the speed of the impeller ( 52 ) of the feed pump ( 35 ) is controllable and / or controllable. High-pressure injection system according to claim 9 or 10, characterized in that the actuator ( 41 ) a flow-controlled slide valve ( 85 ) is with a spool ( 87 ), an elastic valve element ( 80 ), in particular a valve spring ( 81 ), and one, in particular in the spool ( 86 ) integrated, slide channel ( 87 ) and preferably the slide channel ( 87 ) the second outflow channel ( 67 ) and / or the second fuel line ( 33b ). Method for operating a high-pressure injection system ( 36 ), in particular a high-pressure injection system ( 36 ) according to one or more of claims 9 to 13, comprising the steps of: - conveying fuel with a prefeed pump ( 35 ) from a fuel tank ( 32 ) through an inflow workspace ( 63 ), through a downstream working space ( 64 ) and by a first outflow channel ( 66 ) from the effluent working space ( 64 ) and through a first fuel line ( 33a ) to an inlet opening ( 21 ) a high pressure pump ( 1 ), - conveying fuel with the prefeed pump ( 35 ) from the fuel tank ( 32 ) through the inflow workspace ( 63 ), through the Abströmarbeitsraum ( 64 ) and by a second outflow channel ( 67 ) from the effluent working space ( 64 ) and a second fuel line ( 33b ) to a lubricating space ( 40 ) of the high-pressure pump ( 1 ), - Passing of fuel through a bypass channel ( 37 ) from the first outflow channel ( 66 ) and / or the first fuel line ( 33a ) to the inflow channel ( 65 ) and / or to a fuel line ( 33 ) from the fuel tank ( 32 ) into the inflow workspace ( 63 ), with an actuator ( 41 ) passing through the bypass channel ( 37 ) directed volume flow of fuel is controlled changed and / or regulated. A method according to claim 14, characterized in that the volume flow is controlled and / or regulated by, depending on at least one parameter, the volume flow, in particular the flow cross-sectional area for the fuel, on the actuator ( 41 ) is changed, in particular the at least one parameter, the rotational speed of an impeller ( 52 ) of the feed pump ( 35 ) and/ or through the first outflow channel ( 66 ) flowing volume flow of fuel and / or by the second outflow channel ( 67 ) flowing volume flow of fuel and / or the speed of the internal combustion engine ( 39 ) and / or that of the internal combustion engine ( 39 ) requested torque and / or through an inlet channel ( 22 ) of the high-pressure pump ( 1 ) and / or actual volume flow of fuel and / or the fuel with a gear pump ( 14 ), in particular gerotor pump ( 15 ), as prefeed pump ( 35 ) and / or the greater the speed of the impeller ( 52 ) of the feed pump ( 35 ) and / or the larger by the first outflow channel ( 66 ), the smaller the flow cross-sectional area for the fuel on the actuator ( 41 ) and vice versa, in particular the speed of the impeller ( 52 ) of the feed pump ( 35 ) and / or through the first outflow channel ( 66 ) flowing volume flow of fuel indirectly proportional to that by the actuator ( 41 ) guided volume flow of fuel with respect to an identical pressure difference of the fuel to the actuator ( 41 ), in particular indirectly proportional to the flow cross-sectional area for the fuel on the actuator ( 41 ).

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