EP4124745A1 - Pompe haute pression à carburant - Google Patents

Pompe haute pression à carburant Download PDF

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Publication number
EP4124745A1
EP4124745A1 EP22177983.8A EP22177983A EP4124745A1 EP 4124745 A1 EP4124745 A1 EP 4124745A1 EP 22177983 A EP22177983 A EP 22177983A EP 4124745 A1 EP4124745 A1 EP 4124745A1
Authority
EP
European Patent Office
Prior art keywords
pressure
bore
outlet
pump
area
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP22177983.8A
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German (de)
English (en)
Other versions
EP4124745B1 (fr
Inventor
Thomas FROIHOFER
Rainer Kornhaas
Guido Bredenfeld
Stephan Wehr
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP4124745A1 publication Critical patent/EP4124745A1/fr
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Publication of EP4124745B1 publication Critical patent/EP4124745B1/fr
Active legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
    • 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
    • F02M59/462—Delivery valves

Definitions

  • the pump housing comprises a pump body and a pump cover, which are connected to one another, with a damping area belonging to the low-pressure area being delimited by the pump body and the pump cover, in which a diaphragm damper is arranged, wherein the pressure relief valve fluidically connects the high-pressure area to the damping area and opens towards the damping area, so that fuel flows out of the high-pressure area into the damping area when the pressure difference between fuel in the high-pressure area and fuel in the low-pressure area exceeds the opening pressure.
  • the outlet valve is fixed in an outlet valve bore of the pump housing and that the pressure-limiting valve is fixed in a pressure-limiting valve bore of the pump housing.
  • the present invention is based on the desire for a structural design of a high-pressure fuel pump with the features mentioned above, which ensures that the pump is easy to manufacture.
  • outlet valve bore and the pressure-limiting valve bore extend in mutually geometrically parallel planes perpendicular to the longitudinal direction.
  • this facilitates machining, for example machining, of the pump housing to produce the pressure-limiting valve bore and the outlet valve bore, since this machining takes place in mutually parallel planes, in particular in the same plane, and thus, for example, even with the same tool and/or, for example, at the same time can.
  • the pump according to the invention is easier to manufacture than the pump known from the prior art.
  • the outlet is designed as an outlet connector fixed to the pump housing.
  • the outlet has in particular a tubular basic shape and can, for example, on the
  • the pump housing can be welded or screwed together and also in turn comprise means with which a high-pressure line can be tightly fastened to it, for example a thread or the like.
  • 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.
  • outlet valve bore and the pressure-limiting valve bore both start from the outlet connector space. This reduces the number of parts that make up the high-pressure fuel pump and the number of sealing points required in the high-pressure fuel pump.
  • the outlet valve bore extends from the outlet connector space, but not the pressure-limiting valve bore.
  • This has the advantage that a cross-section of the outlet connector space through which flow occurs can be significantly reduced and thus also the cross-section with which the outlet connector is fastened to the pump body.
  • This improves the reliability or pressure resistance with which the outlet port can be attached to the pump housing, because the cross section with which the outlet port is attached to the pump body is proportional to the force that acts on the port when fuel, the is under high pressure, is promoted.
  • the connection length along which the socket can be attached to the pump housing along its circumference is only proportional to the square root of the cross section with which the outlet socket is attached to the pump body.
  • the reduction in the cross-section with which the outlet connector is attached to the pump body which is associated with the measure that only the outlet valve bore extends from the outlet connector space, but not the pressure-limiting valve bore, increases the ratio of the connection length along which the connector extends along its circumference to the Pump housing can be attached to the cross-section with which the outlet port is attached to the pump body.
  • the attachment of the outlet port is able to withstand higher pressures of the fuel being pumped.
  • the pressure-limiting valve bore is closed on the side of its outlet with a ball or a plug, the outlet valve bore being connected to the pressure-limiting valve bore by a high-pressure connection bore located in the high-pressure region.
  • the fluidic communication between the outlet and the pressure-limiting valve then takes place through the high-pressure connection hole only inside the pump housing.
  • a simple and reliable sealing point is realized by closing the pressure relief valve bore with a ball or a plug.
  • the high-pressure connection bore emanates from the damping area and is closed on its outlet side with a ball or a plug. This realizes a relatively short longitudinal extension of the high-pressure connection bore and a further simple and reliable sealing point.
  • outlet valve bore is connected to the pressure relief valve bore by two high-pressure connection bores located in the high-pressure area, with a first high-pressure connection bore starting from the damping area and being closed on its outlet side with a ball or a plug and opens into a second high-pressure connection bore, which in turn opens into the outlet valve bore.
  • the angle at which the first high-pressure connection bore and the second high-pressure connection bore are oriented to one another can be 90°, for example, or between 45° and 135°.
  • the pressure-limiting valve bore is connected to the damping area by a low-pressure connecting bore located in the low-pressure area.
  • the pressure-limiting valve hole and the low-pressure connection hole can, for example, be arranged at right angles to one another; the low-pressure connection bore can, for example, be in Be oriented longitudinally or at an angle of 0 ° to 60 ° to the longitudinal direction.
  • An advantageous design in cases in which a plug is provided that closes the pressure-limiting valve bore and/or a plug is provided that closes the high-pressure connection bore provides that one or both of these plugs is realized with identical components by a valve seat body of the pressure-limiting valve , on which a valve seat of the pressure-limiting valve is formed, which cooperates sealingly with a movable valve element of the pressure-limiting valve. This reduces the number of components composing the high-pressure fuel pump.
  • 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 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 dem Bottom of hole opposite side.
  • 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 the pump body there or emerges from the pump housing or the 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° 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 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 presupply 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 up and down along a longitudinal axis LA running in the longitudinal direction LA, to which the pump piston 18 is axially symmetrical, by means of a drive 36 designed here as a cam disk figure 1 is represented by a double arrow 40 .
  • a drive 36 designed here as a cam disk figure 1 is represented by a double arrow 40 .
  • an outlet valve 37 is arranged to the outlet port 35 and a further downstream Lying high-pressure accumulator 45 ("Rail”) can open towards.
  • 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.
  • figure 2 shows as a first embodiment of the invention, a high-pressure fuel pump 10 in a sectional view.
  • 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 region 28 includes a damper chamber 28a which is connected to the inlet 11 via a fluidic connection not visible in this cross section and which 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 arranged, which can have the shape of a flat and compressible can 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 fixed to the lower portion of the pump body 12a, and a step 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 cooperates with a sealing seat 37.4, which is located on an upstream of the valve element 37.1 sealing seat part 37.2 fixed to the pump is formed.
  • 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. It has a first section 18.1 with a larger diameter, pointing towards the conveying space 16, and a second section 18.2, pointing away from the conveying space, with a smaller diameter (relative to the diameter of the first section 18.1). Between the first and the second section 18.1, 18.2 is one in the figure 2 vertically downward pointing annular step 18.3 formed.
  • 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 made of metal or plastic, for example, as in FIG WO 19 015 862 A1 explained to the applicant in more detail.
  • the high-pressure seal on the other hand, 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 in FIG WO 06 069 819 A1 explained to the applicant in more detail.
  • 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 pump piston 18 is in the in the figure 2 biased downward longitudinal direction LA.
  • 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 arrangement of the pressure-limiting valve 22 in the high-pressure fuel pump 10 according to the invention will now be discussed further by way of example.
  • the invention provides that the pressure relief valve 22 is fixed in a pressure relief valve bore 22a of the pump housing 12 and that the outlet valve bore 37a and the pressure relief valve bore 22a extend in mutually geometrically parallel planes perpendicular to the longitudinal direction LA.
  • the outlet valve bore 37a and the pressure-limiting valve bore 22a are even both oriented in a common plane that is parallel to the longitudinal direction LA, namely in the plane of the drawing figure 2 .
  • outlet valve bore 37a and the pressure-limiting valve bore 22a are even oriented geometrically parallel to one another, namely in figure 2 horizontal direction.
  • outlet valve bore 37a is arranged on the side of the pressure-limiting valve bore 22a facing away from the damping region 28a. In this way, the length of the flow path and thus the flow resistance between the pressure-limiting valve 22 and the damping area 28a is minimized.
  • the pressure-limiting valve bore 22a also extends from the outlet connector chamber 35a, and that the pressure-limiting valve bore 22a is connected to the damping region 28a by a low-pressure connecting bore 28b located in the low-pressure region 28 and oriented in the longitudinal direction LA.
  • the low-pressure connection bore 28b can be coaxial with a longitudinal axis of the high-pressure fuel pump 10 and/or coaxial with a longitudinal axis Axis of symmetry of the pump piston 18 and/or the diaphragm damper 55.
  • the outlet connector 35 extends in particular transversely to the flow direction across the outlet of the pressure relief valve bore 22a and across the outlet of the outlet valve bore 37a, so that the pressure relief valve bore 22a and the outlet valve bore 37a communicate with one another via the outlet connector space 35a arranged between the pump housing 12 and the outlet connector 35.
  • An (external) diameter with which the outlet connector 35 is fixed to the pump housing 12 in this arrangement is relatively large, for example at least as large as the sum of the diameter of the pressure relief valve bore 22a (always: its largest diameter in the case of a stepped bore ) and the diameter of the outlet valve bore 37a (always: its largest diameter in the case of a stepped bore), in particular at least as large as 1.2 times this sum.
  • the cross section of the pressure relief valve bore 22a can be smaller than the cross section of the outlet valve bore 37a.
  • the cross section of the low pressure connection bore 28b can be smaller than the cross section of the pressure relief valve bore 22a, for example by 5% to 35% of the cross section of the pressure relief valve bore 22a.
  • the pressure-limiting valve bore 22a can be embodied as a blind hole into which the low-pressure connecting bore 28b opens, preferably into the bore wall at a point spaced from the bottom of the pressure-limiting valve bore 22a.
  • an axis of the pressure-limiting valve bore 22a intersects an axis of the low-pressure connection bore 28b at a point of intersection, in particular at right angles, which is spaced from the bottom of the pressure-limiting valve bore 22a by at least 0.6 times of the diameter of the low-pressure connection hole 28b is given, in particular by 0.75 times the diameter of the low-pressure connection hole 28b.
  • One The spiral spring 52 of the pressure-limiting valve 22 can then lie against the bottom of the pressure-limiting valve bore 22a without overlapping the mouth of the low-pressure connection bore 28b.
  • the pressure relief valve 22 from the figure 2 (at the same time it can also be about the Figures 4 to 8 act shown pressure relief valve 22) is in the figure 3 enlarged and shown as an example. 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 figure 4 shows a section of a second exemplary embodiment of the invention. It differs from the first exemplary embodiment in that only the outlet valve bore 37a, but not the pressure-limiting valve bore 22a, starts from the outlet connector space 35a. Instead, in this exemplary embodiment, it is provided that the pressure-limiting valve bore 22a is closed on the side of its outlet 22aa with a ball 56, particularly pressed into the pressure-limiting valve bore 22a, or with a plug 57, particularly pressed into the pressure-limiting valve bore 22a, with the outlet valve bore 37a having the Pressure relief valve bore 22a is connected by a high-pressure region 29 lying in the high-pressure connection bore 29a.
  • the high-pressure connection bore 29a starts from the damping area 28a and is provided on its outlet side 29aa with a ball 56, in particular pressed into it, or a ball 56, in particular in they pressed, plug 57 is closed.
  • the outlet connector 35 can be made smaller than in the first exemplary embodiment, for example an (outer) diameter with which the outlet connector 35 is fixed to the pump housing 12 in this arrangement can be smaller than the sum of the diameter of the pressure-limiting valve bore 22a and the diameter of the outlet valve bore 37a, in particular even smaller than 0.9 times this sum.
  • the robustness of the connection of the outlet connector 35 to the pump housing 12 is increased in this way, because while the hydraulic forces acting on the outlet connector 35 are proportional to the cross-sectional area it covers, the connection length with which the outlet connector 35 is fixed to the pump housing 12 is only proportional to the perimeter of the cross-sectional area it covers, i.e. proportional to the square root of the cross-sectional area it covers.
  • the high-pressure connection bore 29a can have a cross section that is smaller than the respective cross sections of the pressure-limiting valve bore 22a, the outlet valve bore 37a and the low-pressure connection bore 28b, for example each at most half as large.
  • An axis of the high-pressure connection bore 29a and the axis of the pressure-limiting valve bore 22a can intersect, in particular intersect at right angles, with an intersection of these axes preferably being at least half a diameter, in particular a full diameter, of the pressure-limiting valve bore 22a away from the outlet of the pressure-limiting valve bore 22a and/or where an intersection of these axes is preferably at least half a diameter, in particular a whole diameter, of the high-pressure connection bore 29a away from the outlet of the high-pressure connection bore 29a.
  • the pressure-limiting valve bore 22a and/or the high-pressure connection bore 29a can be fitted particularly easily on its outlet side 29aa with a ball 56 pressed into it or with a ball 56 pressed into it Plug 57 are closed.
  • the figure 5 shows in part a) a perspective view of a semi-transparent pump body 12a of a high-pressure fuel pump 10 according to the third embodiment of the present invention.
  • the holes explained in detail below are fully recognizable in its interior.
  • part b) shows the figure 5 partially the third embodiment of the invention in a sectional view.
  • the third exemplary embodiment differs from the first two exemplary embodiments in that the outlet valve bore 37a and the pressure-limiting valve bore 22a are not oriented geometrically parallel to one another. Instead, the outlet valve bore 37a and the pressure-limiting valve bore 22a are oriented at an angle that differs from 0° and is at least 20°, for example.
  • the outlet valve bore 37a is connected to the pressure-limiting valve bore 22a by two high-pressure connection bores 29a located in the high-pressure region 29, with a first high-pressure connection bore 29a1 starting from the damping region 28a and having a ball 56 on its output side 29a1a or a plug 57 and opens into a second high-pressure connection bore 29a2, which in turn opens into the outlet valve bore 37a.
  • the high-pressure connection bores 29a1, 29a2 can each have a cross section (their largest diameter in the case of a stepped bore) that is smaller than the respective cross sections of the pressure relief valve bore 22a, the outlet valve bore 37a and the low-pressure connection bore 28b, for example each at most half as large .
  • the two high-pressure connection bores 29a1, 29a2 can under one Be arranged to each other at an angle of at least 20 °, for example 90 °.
  • the first high-pressure connection hole 29a1 can be oriented parallel to the longitudinal direction LA.
  • the second high-pressure connection bore 29a2 can be arranged at an angle to the outlet valve bore 37a which is at least 20° and, for example, at most 70°.
  • the figure 6 shows a fourth embodiment of the invention. It differs from the one related to the figure 2 and 3 explained first exemplary embodiment in that the low-pressure connection bore 28b is not oriented in the longitudinal direction LA, but rather at an angle other than 0°, for example at least 20°, for example up to 60°.
  • the pump body 12a has a recess 13 on the side facing the damping area 28a and the low-pressure connection bore 28b opens into the recess 13 or extends from the recess 13 in such a way that the recess 13 in the flow cross-section is wider than the low-pressure connection bore 28b, for example with regard to the flow cross-section at least twice as wide or at least three times as wide.
  • the figure 7 shows a fifth embodiment of the invention. It differs from the one related to the Figures 3 and 4 explained second embodiment characterized in that the low-pressure connection bore 28b is not oriented in the longitudinal direction LA, but at an angle other than 0 °, for example at least 20 °, for example up to 60 °.
  • the pump body 12a has a recess 13 on the side facing the damping area 28a and the low-pressure connection bore 28b opens into the recess 13 or extends from the recess 13 in such a way that the recess 13 in the flow cross-section is wider than the low-pressure connection bore 28b, for example with regard to the flow cross-section at least twice as wide or at least three times as wide.
  • the plug 57 which closes the pressure-limiting valve bore 22a, is also the high-pressure connection bore 29a closes, ie with the plug 57, which closes the high-pressure connection bore 29a, is identical in terms of component.
  • this component is also part of the pressure-limiting valve 22 , for example the valve-seat body 38 of the pressure-limiting valve 22 .
  • the figure 8 shows a sixth embodiment of the invention. It differs from the one related to the Figures 3 and 4 explained second embodiment of the invention characterized in that 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 to its outlet 22aa, in which figure 8 left, and a second section 22.3, which has a smaller diameter and points to the low-pressure connection bore 28b, in which figure 8 right, and with an annular step 22.2 formed between the first section 22.1 and the second section 22.3, the spiral spring 52 being supported on the annular step 22.2.
  • 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 to its outlet 22aa, in which figure 8 left, and a second section 22.3, which has a smaller diameter and points to the low-pressure connection bore 28b, in which figure 8 right, and with an annular step 22.2 formed between the first section 22.1 and the second section 22.3, the spiral spring 52
  • the cross section of the first section 22.1 can, for example, be at least twice as large as the cross section of the second section 22.3.
  • the pump body 12a has a recess 13 on the side facing the damping area 28a and the low-pressure connection bore 28b opens into the recess 13 in such a way or extends from the recess 13 in such a way that the recess 13 is wider in the cross-section through which flow occurs than the low-pressure connecting bore 28b, for example with regard to the cross-section through which flow occurs, at least twice as wide or at least three times as wide.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP22177983.8A 2021-07-28 2022-06-09 Pompe haute pression à carburant Active EP4124745B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021208122.3A DE102021208122A1 (de) 2021-07-28 2021-07-28 Kraftstoff-Hochdruckpumpe

Publications (2)

Publication Number Publication Date
EP4124745A1 true EP4124745A1 (fr) 2023-02-01
EP4124745B1 EP4124745B1 (fr) 2024-09-11

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ID=82016566

Family Applications (1)

Application Number Title Priority Date Filing Date
EP22177983.8A Active EP4124745B1 (fr) 2021-07-28 2022-06-09 Pompe haute pression à carburant

Country Status (4)

Country Link
EP (1) EP4124745B1 (fr)
KR (1) KR20230017741A (fr)
CN (2) CN218882498U (fr)
DE (1) DE102021208122A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006069819A1 (fr) 2004-12-28 2006-07-06 Robert Bosch Gmbh Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne
DE10327411B4 (de) * 2002-10-15 2015-12-17 Robert Bosch Gmbh Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
EP2344749B1 (fr) 2008-10-28 2016-05-04 Robert Bosch GmbH Pompe haute pression à carburant pour un moteur à combustion interne
WO2019015862A1 (fr) 2017-07-20 2019-01-24 Robert Bosch Gmbh Pompe à piston
DE102019203967A1 (de) * 2018-03-27 2019-10-02 Keihin Corporation Ventileinheit-befestigungsstruktur und fluidpumpe welche selbige verwendet
WO2022063521A1 (fr) * 2020-09-22 2022-03-31 Robert Bosch Gmbh Pompe à carburant haute pression pour système d'injection de carburant d'un moteur à combustion interne

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10327411B4 (de) * 2002-10-15 2015-12-17 Robert Bosch Gmbh Druckbegrenzungsventil sowie Kraftstoffsystem mit einem solchen Druckbegrenzungsventil
WO2006069819A1 (fr) 2004-12-28 2006-07-06 Robert Bosch Gmbh Pompe a piston, notamment pompe a carburant haute pression destinee a un moteur a combustion interne
EP2344749B1 (fr) 2008-10-28 2016-05-04 Robert Bosch GmbH Pompe haute pression à carburant pour un moteur à combustion interne
WO2019015862A1 (fr) 2017-07-20 2019-01-24 Robert Bosch Gmbh Pompe à piston
DE102019203967A1 (de) * 2018-03-27 2019-10-02 Keihin Corporation Ventileinheit-befestigungsstruktur und fluidpumpe welche selbige verwendet
WO2022063521A1 (fr) * 2020-09-22 2022-03-31 Robert Bosch Gmbh Pompe à carburant haute pression pour système d'injection de carburant d'un moteur à combustion interne

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CN115681127A (zh) 2023-02-03
DE102021208122A1 (de) 2023-02-02
EP4124745B1 (fr) 2024-09-11
CN218882498U (zh) 2023-04-18

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