Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
  • F02M63/0012—Valves
  • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
  • F02M63/005—Pressure relief valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
  • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
  • F02M59/025—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by a single piston
  • F02M59/027—Unit-pumps, i.e. single piston and cylinder pump-units, e.g. for cooperating with a camshaft
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
  • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
  • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
  • F02M59/46—Valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
  • F02M63/0003—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure
  • F02M63/0005—Fuel-injection apparatus having a cyclically-operated valve for connecting a pressure source, e.g. constant pressure pump or accumulator, to an injection valve held closed mechanically, e.g. by springs, and automatically opened by fuel pressure using valves actuated by fluid pressure
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B19/00—Machines or pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B1/00 - F04B17/00
  • F04B19/04—Pumps for special use
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
  • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
  • F04B53/16—Casings; Cylinders; Cylinder liners or heads; Fluid connections

Definitions

• a high-pressure fuel pump with an inlet for supplying fuel, with an outlet for dispensing compressed fuel, with a pump housing, a pumping chamber arranged in the pump housing, with a pump piston that can be displaced in the pump housing in a longitudinal direction and delimits the delivery chamber, with an inlet valve that is arranged between the inlet and the delivery chamber and opens towards the delivery chamber, with an outlet valve that is arranged between the delivery chamber and the outlet and opens away from the delivery chamber a high-pressure area that extends fluidly between the outlet valve and the outlet, with a low-pressure area that extends fluidly between the inlet and the inlet valve, and with a pressure relief valve that fluidly connects the high-pressure area to the low-pressure area and opens to the low-pressure area, so that fuel flows off from the high-pressure area into the low-pressure area when the pressure difference between fuel in the high-pressure area and fuel in the low-pressure area exceeds an opening
• the pump piston is designed as a stepped piston, with a first section which faces the delivery chamber and has a larger diameter, and a second section which has a smaller diameter and points away from the pumping chamber, with a high-pressure seal being arranged between the first section and the pump housing, in which the pump piston can be displaced and which separates the pumping chamber from the low-pressure region, with a low-pressure seal being arranged between the second section and a seal carrier fixed to the pump housing , which separates the low-pressure area from the space outside the high-pressure fuel pump, with a stepped space of the low-pressure area being located between the seal carrier and the pump housing, wherein the pressure relief valve fluidly connects the high-pressure area to the step room of the low-pressure area and opens towards the step room, so that fuel flows out of the high-pressure area into the step room when the pressure difference between fuel in the high-pressure area and fuel in the low-pressure area exceeds an opening pressure,
• the pressure-limiting valve has a valve seat body which is pressed into the pressure-limiting valve bore and on which a conical valve seat is formed, the pressure-limiting valve having a valve element which has the shape of a sphere and which the valve seat comes into sealing contact, the valve element being pressed in the closing direction by a holding element, the holding element being pressed in the closing direction by a spiral spring.
• the pressure-limiting valve is designed as a blind hole in the pump body
• Pressure relief valve bore is arranged, which emanates from the step chamber and that the spiral spring is supported on a separate pressed into the pressure relief valve bore part.
• the invention is based on the desire to make the high-pressure fuel pump simple and efficient to manufacture.
• the implementation of the pressure relief valve bore as a blind hole in the pump body, which starts from the step chamber, has proven to be disadvantageous in that a separate, flow-through part is required, which must be pressed into the pressure relief valve bore in a separate assembly step during assembly of the pressure relief valve in order to Support spiral spring, with the case generated in the spiral spring and the closing force acting on the valve element or on the valve seat defines the opening pressure of the pressure-limiting valve, i.e. it must be adjustable quite precisely.
• the solution according to the invention differs from the previously known solution in that the pressure-limiting valve is arranged in a pressure-limiting valve bore designed as a through-bore through the pump body, with the pressure-limiting valve bore extending from the damping area to the step chamber and on the side facing the damping area by a pressure relief valve bore is closed by a pressed ball or a plug pressed into the pressure relief valve bore; and that the pressure relief valve bore is designed as a stepped bore, with a first section which has a larger diameter and faces towards the damping area, and a second section which has a smaller diameter and faces towards the step room, and with a between the first section and the second section formed annular step on which the spiral spring is supported.
• the pressure-limiting valve of the pump according to the invention can be installed in a simple and efficient manner from the side of the pump housing facing the damping chamber, preferably with the spiral spring first, so that it comes into contact with the annular step. After the pressure-limiting valve has been installed in the pressure-limiting valve bore, the latter can easily be closed on the side facing the damping area by pressing in a ball or a plug.
• the outlet valve is arranged in an outlet valve bore of the pump housing, with the outlet valve bore and the pressure-limiting valve bore intersecting, in particular at right angles. In this way, the integration of the pressure-limiting valve in the high-pressure area is accomplished without any additional high-pressure sealing point and in a manner that saves installation space.
• the outlet valve has a movable valve element and a sealing seat part arranged upstream of the valve element, which is fixed to the pump with a sealing seat part fixing section, and on which a sealing seat part with the valve element cooperating sealing seat is formed, and has a pump-fixed counter-plate arranged downstream of the valve element, which is fixed in a pump-fixed manner with a counter-plate fixing section and which limits the mobility of the valve element in the downstream direction, the pressure-limiting valve bore opening the outlet valve bore between the sealing-seat part fixing section and the counter-plate fixing section cuts.
• the pressure-limiting valve bore then intersects the space in which the components belonging to the outlet valve are mounted, so that this space has a dual use, so to speak.
• the outlet socket space can consist of or comprise the part of the interior space of the socket pointing towards the pump housing.
• the outlet connector space can also include a recess in the pump body that is covered by the outlet connector, and in particular can consist of these two partial spaces.
• the outlet socket space can consist of the recess in the pump body covered by the outlet socket.
• the outlet to be in the form of an outlet connector fixed to the pump housing and for an outlet connector space to be formed between the pump housing and the outlet connector, with the outlet valve being fixed in an outlet valve bore of the pump housing, with the outlet valve bore starting from the outlet connector space, with the Pressure-limiting valve hole is connected to the outlet connector space via a high-pressure connection hole located in the high-pressure area, which starts from the outlet connector space.
• the flexibility of the arrangement of the pressure-limiting valve bore in the pump body is increased compared to the previously described solution.
• outlet valve bore and the high-pressure connection bore are arranged parallel to one another and, for example, perpendicularly to the longitudinal direction, they can easily be produced, for example with the same tool or together.
• the space available in the pump body for inner contours can be optimally used - or the pump body can potentially be further reduced in size.
• Central axis of the pump piston i.e. the longitudinal axis, intersects.
• the fuel can then flow out of the pumping chamber and through the outlet valve without further deflection and in this respect with particularly low friction.
• an imaginary (possibly extended) central axis of the outlet valve bore does not intersect an imaginary (possibly extended) central axis of the pump piston, i.e. the longitudinal axis.
• a high-pressure fuel pump for a fuel system for an internal combustion engine with an inlet for supplying fuel, with an outlet for dispensing compressed fuel, with a pump housing, a pumping chamber arranged in the pump housing, with a pump piston that can be displaced in the pump housing along a longitudinal direction and delimits the delivery chamber, with an inlet valve that is arranged between the inlet and the delivery chamber and opens towards the delivery chamber, with an outlet valve that is arranged between the delivery chamber and the outlet and opens away from the delivery chamber, with a High-pressure area that extends fluidly between the outlet valve and the outlet, with a low-pressure area that extends fluidly between the inlet and the inlet valve, and with a pressure relief valve that fluidly connects the high-pressure area with the low-pressure area and opens toward the low-pressure area, so that fuel flows out of the high-pressure area into the low-pressure area when the pressure difference between fuel in the high-pressure area and fuel in the low-pressure area
• a high-pressure fuel pump for a fuel system for an internal combustion engine with an inlet for supplying fuel, with an outlet for dispensing compressed fuel, with a pump housing, a pumping chamber arranged in the pump housing, with a A pump piston that can be displaced in the pump housing along a longitudinal direction and delimits the pumping chamber, with an inlet valve that is arranged between the inlet and the pumping chamber and opens towards the pumping chamber, with an outlet valve that is arranged between the pumping chamber and the outlet and opens away from the pumping chamber, with a high-pressure area , which extends fluidly between the outlet valve and the outlet, with a low-pressure area, which extends fluidly between the inlet and the inlet valve, and with a pressure relief valve, which fluidly connect
• the second further object can be advantageously further developed, preferably with the feature that the outlet valve bore and the high-pressure connection bore both emanate from the outlet connector space.
• the bores can then be made in a simple manner, e.g. with the same tool.
• the second further object can also be advantageously further developed with the features of claims 7 or 8 and/or with the features disclosed in FIG. 7 and/or in the description referring to it.
• a bore in particular outlet valve bore, pressure-limiting valve bore, low-pressure connection bore, high-pressure connection bore, etc.
• the bore has an axial symmetry whose axis of symmetry corresponds to the axis of rotation of the twist drill. This axis of symmetry then indicates the direction in which the hole is oriented.
• the bore can basically be a through bore through the pump housing or the pump body or a blind bore which ends at a bore bottom arranged in the pump housing or in the pump body.
• the exit of a bore In the context of the present invention, this is the side of the bore that is first produced by machining when the drill penetrates into the pump housing or the pump body. In the case of blind holes, this is always the side opposite the bottom of the hole.
• the mouth of a bore is therefore the side of the bore opposite the outlet of a bore if the bore meets another inner contour of the pump housing or pump body there or emerges from the pump housing or pump body.
• the bores of the present invention are free of undercuts, particularly when viewed from their exit.
• the bore wall in a through bore is the inner contour represented by the through bore;
• the wall of the hole is that part of the inner contour represented by the through hole that is not the bottom of the hole.
• the high-pressure area is understood to be the entire space that communicates with the outlet easily, in particular without further interposed valves, so that a uniform pressure is established in the high-pressure area, for example 500 bar when the pump is in operation.
• the low-pressure area is understood to mean the entire space that communicates with the inlet without further ado, in particular without further interposed valves, so that a uniform pressure is established in the low-pressure area during operation of the pump and when the pump is connected to the inlet Low pressure pump for example 5 bar.
• the inner contours of the high-pressure fuel pump through which fuel flows finally consist of the low-pressure area, the pumping chamber and the high-pressure area. These areas are separated from each other by the inlet valve, the outlet valve and the pressure relief valve.
• the fuel can be, for example, a fuel such as gasoline.
• an angle different from 0° is used within the scope of the invention, it can be an angle that differs significantly from 0°, that is, for example, is at least 2° or at least 5°.
• it can be an angle between 2° and 90°.
• FIG. 1 shows a simplified schematic representation of a fuel system for an internal combustion engine.
• FIG. 2 shows a first exemplary embodiment of the invention.
• FIG. 3 shows a detailed example of a pressure-limiting valve, as can be used in the exemplary embodiments.
• FIG. 4 shows a second exemplary embodiment of the invention.
• FIG. 5 shows a third exemplary embodiment of the invention.
• FIG. 6 shows a fourth exemplary embodiment of the invention.
• FIG. 7 shows a fifth exemplary embodiment of the invention.
• FIG. 1 shows a fuel system 1 for an internal combustion engine (not shown further) in a simplified schematic representation.
• fuel is supplied from a fuel tank 2 via a suction line 4 by means of a pre-supply pump 6 and a low-pressure line 8 via an inlet connection 20 to a high-pressure fuel pump 10 designed as a piston pump.
• An inlet valve 14 is arranged fluidically downstream of the inlet connection piece 20 .
• a low-pressure region 28 of the high-pressure fuel pump 10 is located fluidically between the inlet connection 20 and the inlet valve 14.
• a delivery chamber 16 of the high-pressure fuel pump 10 is located downstream of the inlet valve 14. Pressure pulsations in the low-pressure region 28 can be damped by means of a pressure damper device.
• the inlet valve 14 can be forced open via an actuating device designed here as an electromagnetic actuator 30 .
• the actuating device and thus the intake valve 14 can be controlled via a control unit 32 .
• a pump piston 18 of the high-pressure fuel pump 10 can be moved along an in The longitudinal axis LA running in the longitudinal direction, with respect to which the pump piston 18 is axially symmetrical, can be moved up and down, which is illustrated by a double arrow 40 in FIG.
• An outlet valve 37 is arranged fluidically between the pumping chamber 16 and an outlet connection 35 of the high-pressure fuel pump 10 and can open towards the outlet connection 35 and a high-pressure accumulator 45 (“rail”) located further downstream.
• a high-pressure region 29 of the high-pressure fuel pump 10 extends fluidically between the outlet valve 37 and the outlet connection piece 35 .
• the high-pressure area 29 and the low-pressure area 28 are directly connected to one another via a pressure-limiting valve 22, which opens when a limit pressure is exceeded in the high-pressure area 29 of the high-pressure fuel pump 10 or in the high-pressure accumulator 45 communicating with it.
• the pressure-limiting valve 22 is designed as a spring-loaded check valve and can open toward the low-pressure area 28 of the high-pressure fuel pump 10 . In this way, the pressure that can be generated by the high-pressure fuel pump 10 in the high-pressure accumulator 45 is limited.
• FIG. 2 shows a sectional view of a high-pressure fuel pump 10 as a first exemplary embodiment of the invention.
• the high-pressure fuel pump 10 has an inlet 11 designed as an inlet connection piece 20 .
• the inlet 11 communicates with the entire low-pressure area 28 of the high-pressure fuel pump 10 without the interposition of valves.
• the high-pressure fuel pump 10 has an outlet 34 designed as an outlet connector 35 .
• the outlet 34 communicates with the entire high-pressure area 29 of the high-pressure fuel pump 10 without the interposition of valves.
• the outlet connector 35 and the inlet connector 20 are fixed to a pump housing 12 in which a pumping chamber 16 is also arranged, which is delimited by a pump piston 18 that can be displaced along a longitudinal direction LA.
• the low-pressure area 28 includes a damper chamber 28a, which has an in The fluidic connection, which is not visible in this cross section, is connected to the inlet 11 and is formed between a pump body 12a of the pump housing 12 and a pump cover 12b of the pump housing 12 .
• a membrane damper 55 is arranged in the damping space 28a, which can have the shape of a flat and compressible box formed by two metal membranes.
• the non-visible fluidic connection between the inlet 11 and the damper chamber 28a can, for example, comprise a filter bore in which a filter element is arranged, which frees a fuel flowing through the filter bore from entrained solid particles above a minimum size.
• a seal carrier 60 is fastened to the lower section of the pump body 12a in FIG. 2, and a stepped space 28d is formed between the pump body 12a and the seal carrier 60.
• the stepped space 28d communicates with the damping space 28a via a through hole, which is not visible in this cross section, through the pump body 12a and is therefore part of the low-pressure region 28.
• the conveying chamber 16 is delimited towards the low-pressure region 28 by an inlet valve 14 that opens toward the conveying chamber 16 when there is a corresponding pressure difference.
• the inlet valve 14 can be forced open by a tappet 31 driven by the actuator 30 .
• the actuator 30 has an actuator housing 30a which is fixed to the pump housing 12 and in which an electromagnetic coil 30b is arranged, which can be energized via an externally accessible electrical connection 30c of the high-pressure fuel pump 10 .
• An inlet valve area 28c of the low-pressure area 28 is formed geometrically between the inlet valve 14 and the actuator 30 in the pump housing. It communicates with the damping area 28a via the bore 28f visible in this cross section.
• the delivery chamber 16 is delimited towards the high-pressure region 29 by an outlet valve 37 which opens away from the delivery chamber 16 when there is a corresponding pressure difference.
• it is arranged in an outlet valve bore 37a of the pump housing 12 or of the pump body 12a. It has a movable valve element 37.1 which interacts with a sealing seat 37.4 which is formed on a sealing seat part 37.2 which is arranged fixed to the pump upstream of the valve element 37.1.
• the mobility of the valve element 37.1 in the downstream direction is limited by a counterplate 37.5 fixed to the pump.
• the outlet valve bore 37a starts from an outlet connection space 35a located between the outlet connection 35 and the pump housing 12 or the pump body 12a.
• the pump piston 18 is designed as a stepped piston. Has a first section 18.1 with a larger diameter, pointing towards the conveying chamber 16, and a second section 18.2, pointing away from the conveying chamber, with a smaller diameter (relative to the diameter of the first section 18.1). An annular step 18.3 pointing vertically downwards in FIG. 2 is formed between the first and the second section 18.1, 18.2.
• a high-pressure seal 80 in which the pump piston 18 can be displaced, is arranged between the first section 18.1 and the pump housing 12.
• the high-pressure seal 80 separates the pumping chamber 16 from the low-pressure area 28 in a sealing manner.
• the high-pressure seal 80 can, for example, be a separate sealing ring, e.g. made of metal or plastic, for example as explained in more detail in the applicant's WO 19015862 A1.
• the high-pressure seal 80 can also be a narrow gap extending over a certain length between the pump piston 18 and a bushing or between the pump piston 18 and the pump housing 12, for example as explained in more detail in the applicant's WO 06069819 A1.
• a low-pressure seal 78 is arranged between the second section 18.2 and the seal carrier 60 already mentioned above, which seal separates the stepped space 28d of the low-pressure region 28 from the space 100 that is located outside of the high-pressure fuel pump 10.
• the pump piston 18 can be displaced in the low-pressure seal 78 .
• the high-pressure fuel pump 10 has a pressure-limiting valve 22, which fluidly connects the high-pressure area 29 to the low-pressure area 28 and opens towards the low-pressure area 28, so that fuel flows out of the high-pressure area 29 into the low-pressure area 28 when the pressure difference between fuel in the high-pressure area 29 and fuel in the low pressure region 28 exceeds a cracking pressure.
• the pressure-limiting valve is shown in detail and as an example in FIG. It has a valve seat body 38 which is pressed into the pressure relief valve bore 22a or into a housing of the pressure relief valve 22 and on which a conical valve seat 42 is formed.
• the pressure-limiting valve 22 also has a valve element 44 which has the shape of a sphere and which comes into sealing contact with the valve seat 42 .
• the valve element 44 is pressed in the closing direction by a holding element 46 and the holding element 46 is pressed in the closing direction by a coil spring 52 .
• the spiral spring 52 is supported on a housing of the pressure relief valve 22 or directly on the pump housing 12 .
• the spiral spring 52 is in contact with a radially outer area 464 of the holding element 46 .
• a radially inner area 465 of the holding element 46 is received by the spiral spring 52 .
• the opening pressure of the pressure limiting valve 22 is defined by the rigidity of the coil spring 52 and by the area effective on the pressure limiting valve 22, and thus at the same time the maximum pressure difference that the high-pressure fuel pump 10 is able to generate between its inlet 11 and its outlet 34.
• the pressure-limiting valve 22 fluidly connects the high-pressure area 29 with the step room 28d of the low-pressure area 28 and opens towards the step room 28d, so that fuel flows out of the high-pressure area 29 into the step room 28d when the Pressure difference between fuel in the high-pressure area 29 and fuel in the low-pressure area 28 a opening pressure, and that the pressure relief valve 22 is arranged in a pressure relief valve bore 22a designed as a through bore through the pump body 12b, the pressure relief valve bore 22a extending from the damping area 28a to the step chamber 28d and on the side facing the damping area 28a through a hole in the pressure relief valve bore 22a pressed ball 56 or a pressed into the pressure relief valve bore 22a plug 57 is closed, wherein the
• Pressure relief valve bore 22a is designed as a stepped bore, with a first section 22.1, which has a larger diameter and points toward the damping area 28a, and a second section 22.3, which has a smaller diameter and points toward the stepped chamber 28d, and with a between the first section 22.1 and the second section 22.3 formed annular step 22.2 and that the above-mentioned spiral spring 52 of the pressure relief valve 22 is supported on the annular step 22.2 of the pressure relief valve bore 22a.
• the outlet valve bore 37a and the pressure-limiting valve bore 22a intersect, in particular at right angles.
• the cut is made within the high-pressure area 29.
• the cut is made in such a way that the sealing seat part 37.2 is fixed to the pump with a sealing seat part fixing section 37.3 and that the counter-plate 37.5 is fixed to the pump with a counter-plate fixing section 37.6 and that the pressure-limiting valve bore 22a has the outlet valve bore 37a between the sealing seat part -Fixing section 37.3 and the counter-plate fixing section 37.6 intersects.
• an imaginary center axis of the outlet valve bore 37a intersects an imaginary center axis of the pump piston 18, and consequently the longitudinal axis of the high-pressure gasoline pump.
• FIG. 4 A second exemplary embodiment of the invention is shown in FIG. 4 in part a) in a sectional view in part and in part b) based on a plan view of the pump body 12a shown semi-transparent.
• the second embodiment differs from the first embodiment in that there is no provision for the outlet valve bore 37a and the pressure relief valve bore 22a to intersect. Instead, it is provided in the second embodiment that the
• Pressure-limiting valve bore 22a is connected to the outlet connector space 35a via a high-pressure connection hole 29a located in the high-pressure area 29 and emanating from the outlet connector space 35a.
• the outlet valve bore 37a and the high-pressure connection bore 29a are arranged at an angle different from 0°, in particular at an angle of at least 20°, to one another and in each case perpendicular to the longitudinal direction LA.
• An imaginary center axis of the outlet valve bore 37a intersects in particular an imaginary center axis of the pump piston 18.
• FIG. 5 A third exemplary embodiment of the invention is shown in FIG. 5 in part a) in a sectional representation of a detail and in part b) based on a plan view of the pump body 12a, which is represented semi-transparently.
• the third embodiment differs from the second embodiment in that the outlet valve bore 37a and the high-pressure communication bore 29a are arranged in parallel with each other.
• these two bores 22a, 37a are arranged perpendicular to the longitudinal direction LA.
• An imaginary center axis of the outlet valve bore 37a does not or not necessarily intersect an imaginary center axis of the pump piston 18 .
• a fourth exemplary embodiment of the invention is designed in accordance with the first independent claim and is shown in a sectional illustration in FIG. It is a high-pressure fuel pump 10 for a fuel system for an internal combustion engine, with an inlet 11 for supplying fuel, with an outlet 34 for dispensing compressed fuel, with a pump housing 12, a delivery chamber 16 arranged in the pump housing, with a pump piston 18 which can be displaced in the pump housing 12 along a longitudinal direction LA and delimits the delivery chamber, with an inlet valve 14 which is arranged between the inlet 11 and the delivery chamber 16 and which opens towards the delivery chamber 16, with an outlet valve which is arranged between the delivery chamber 16 and the outlet 34 37, which opens away from the pumping chamber 16, with a high-pressure area 29, which extends fluidically between the outlet valve 20 and the outlet 34, with a low-pressure area 28, which extends fluidically between the inlet 11 and the inlet valve 14, and with a pressure-limiting valve 22 , which fluidly connects the high-pressure area 29 to the low-pressure area 28 and opens
• a fifth exemplary embodiment of the invention is designed according to the second independent claim and is shown in part a) in a sectional view in part and in part b) based on a plan view of the semi-transparent pump body 12a in FIG.
• It is a high-pressure fuel pump 10 for a fuel system for an internal combustion engine, with an inlet 11 for supplying fuel, with an outlet 34 for dispensing compressed fuel, with a pump housing 12, a delivery chamber 16 arranged in the pump housing, with a in the pump housing 12 along a longitudinal direction LA displaceable pump piston 18, which delimits the delivery chamber, with an inlet valve 14 arranged between the inlet 11 and the delivery chamber 16, which opens towards the delivery chamber 16, with an outlet valve 37 arranged between the delivery chamber 16 and the outlet 34 , which opens away from the pumping chamber 16, with a high-pressure area 29, which extends fluidically between the outlet valve 20 and the outlet 34, with a low-pressure area 28, which extends fluidically between the inlet 11 and the inlet valve 14, and with a pressure-limiting
• Pressure relief valve bore 22a is arranged in the pump housing 12, which runs in the longitudinal direction LA and, starting from the step chamber 28d, opens into a high-pressure connection bore 29a in the pump housing 12, which is arranged in the high-pressure area 29 and at an angle other than 0°, for example at an angle from 5° to 15°, to which
• outlet valve bore 37a with outlet 34 in particular being embodied as an outlet port 35 fixed to pump housing 12, with an outlet port chamber 35a being formed in particular between pump housing 12 and outlet port 35, and with outlet valve bore 37a and high-pressure connection bore 29a in particular being both emanate from the outlet connection space 35a.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Physics & Mathematics (AREA)
• Fluid Mechanics (AREA)
• Fuel-Injection Apparatus (AREA)

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• 2021
  • 2021-07-28 DE DE102021208117.7A patent/DE102021208117A1/de active Pending
• 2022
  • 2022-06-09 US US18/292,576 patent/US20240344492A1/en active Pending
  • 2022-06-09 EP EP22732207.0A patent/EP4377566A1/de active Pending
  • 2022-06-09 CN CN202280065651.1A patent/CN118043547A/zh active Pending
  • 2022-06-09 JP JP2024505203A patent/JP2024528028A/ja active Pending
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