EP1353071A2 - Système de contrôle de capacité d'une pompe à combustible - Google Patents

Système de contrôle de capacité d'une pompe à combustible Download PDF

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Publication number
EP1353071A2
EP1353071A2 EP02027253A EP02027253A EP1353071A2 EP 1353071 A2 EP1353071 A2 EP 1353071A2 EP 02027253 A EP02027253 A EP 02027253A EP 02027253 A EP02027253 A EP 02027253A EP 1353071 A2 EP1353071 A2 EP 1353071A2
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
pressure fuel
fuel pump
control
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.)
Withdrawn
Application number
EP02027253A
Other languages
German (de)
English (en)
Other versions
EP1353071A3 (fr
Inventor
Uwe Liskow
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
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1353071A2 publication Critical patent/EP1353071A2/fr
Publication of EP1353071A3 publication Critical patent/EP1353071A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
    • 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
    • F04B49/12—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 varying the length of stroke of the working members
    • F04B49/121—Lost-motion device in the driving mechanism

Definitions

  • the invention relates to a high-pressure fuel pump for an injection system of internal combustion engines, with at least two pump elements for delivery to delivery of fuel into a high pressure connection.
  • Such high-pressure fuel pumps are, for example, as Axial piston pumps, radial piston pumps or Series injection pumps are known.
  • the invention has for its object a Provide high-pressure fuel pump, its delivery rate is easy to regulate.
  • the efficiency of the High-pressure fuel pump according to the invention in all Load points should be approximately the same.
  • This task is for a high pressure fuel pump for an injection system of internal combustion engines, with at least two pump elements to promote Solved fuel in a high pressure connection in that A controllable one at least between two pump elements hydraulic connection is provided.
  • the controllable hydraulic connection between the Pump elements ensures that in partial load operation Pump element, which is in the delivery stroke, one Partial quantity in the pump element promotes itself in the Suction stroke is located. This reduces the required Pump work and it only gets the amount of fuel needed brought to the injection pressure. This is the Efficiency of the high-pressure fuel pump according to the invention Relatively good even in the partial load range.
  • the hydraulic connection through at least one switching valve or at least one control valve be controlled controlled.
  • Switching valves the efficiency of the invention High pressure fuel pump further increased as the hydraulic connection with the switching valve open has low flow resistance.
  • Control valve a longitudinal slide in a housing has control slots in the housing are hydraulically connected to the pump elements stand, and that the overlap of longitudinal slide and Control slots is adjustable so that the desired throttle effect in the control valve on simple and effective way.
  • control valve has a longitudinal slide guided in a housing, that control grooves are formed in the longitudinal slide, that in the housing holes that are with the pump elements are hydraulically connected, are in place, and that the hydraulic connection between the holes the longitudinal slide is adjustable.
  • a High-pressure fuel pump provides that the control valve is in sync with the pump elements driven rotary valve that in the Rotary valve a hydraulic connection is provided that the hydraulic connection has one at each end Tax groove shows that the tax grooves with Control slots in a housing of the control valve interact that the control slots with the Pump elements are hydraulically connected, and that the coverage of control grooves and control slots is adjustable.
  • the Adjust the delivery rate particularly sensitively. this applies especially when the phase shift of the Control grooves and the control slots and the Phase shift of the pump elements of the High pressure fuel pump match.
  • the High pressure fuel pump a first membrane on each Have pump element that have a delivery chamber Pump elements limited, and the controllable hydraulic Connection connect the delivery areas of the pump elements.
  • the Advantages of a diaphragm pump known per se also for one High pressure fuel pump according to the invention made usable become.
  • the High pressure fuel pump a second membrane on each Has pump element, the second membrane each one Pressure chamber delimited from the pumping chambers of the pump elements and the controllable hydraulic connection the pressure rooms the pump elements connects.
  • the pressure rooms one can Pressure fluid, especially an oil, as the working medium be present and the piston of the pump elements through the second membranes on the pressure fluid in the pressure rooms Act.
  • This measure is only in the Delivery chambers fuel, so that in the pressure chamber and in the pump elements, in particular between the piston and Cylinder of the pump elements, a suitable pressure fluid, which preferably has good lubricating properties and not prone to cavitation, present.
  • the high-pressure fuel pump according to the invention can advantageously also in connection with a common rail be used.
  • common rail fuel injection systems is the regulation of Delivery volume and thus also the pressure in the common rail of great importance, so that the advantages of the invention are particularly positive in such injection systems to make noticable.
  • Fig. 1 is a first embodiment High-pressure fuel pump according to the invention for a Injection system of internal combustion engines schematically shown.
  • the High-pressure fuel pump 1 as an axial piston pump educated.
  • the longitudinal section according to FIG. 1 there are two Pump elements 3 recognizable, which are from a swash plate 5 are driven in a manner known per se.
  • the Swash plate 5 in turn is driven by a drive shaft 7 driven.
  • the pump elements 3 essentially consist of a Pump piston 9, which is guided in a cylinder bore 11 is.
  • the pump piston 9 On the end facing away from the swash plate 5 the pump piston 9 are a first membrane 13 and a second membrane 15 arranged.
  • the first membrane 13 separates one filled with fuel (not shown) Delivery chamber 17 from the rest of the pump element 3.
  • the delivery rooms are connected via a low pressure connection 19 17 during the suction stroke of the pump piston 9 with fuel filled.
  • a first Check valve 21 arranged.
  • the one from the pump elements 3 funded during the delivery stroke from the delivery rooms 17 Fuel enters via second check valves 23 a high pressure connection 25.
  • the high pressure connection 25 can, for example, a common rail, not shown or injectors (also not shown) with under High-pressure fuel can be supplied.
  • the pressure chambers 27 can with a Pressure fluid (not shown), especially oil, filled his.
  • a Pressure fluid (not shown), especially oil, filled his.
  • the use of a special pressure fluid can because of its favorable tribological properties and low tendency to cavitation may be advantageous.
  • the Pump piston 9 can be of pressure fluid, especially oil, be surrounded so that the lubrication of the pump piston 9 in the cylinder bore 11 and the swash plate 5 always is guaranteed.
  • a hydraulic connection 29 between the pressure chambers 27a and 27b of the pump elements 3 are provided.
  • the hydraulic connection 29 can in the embodiment 1 as a bore in a housing 31 of the High-pressure fuel pump 1 may be formed.
  • the control valve 33 can also be used as Switch valve to be formed.
  • the hydraulic connection 29 Through the control valve 33 can the hydraulic connection 29 completely if necessary be closed, so that the invention High-pressure fuel pump 1 like one from the prior art Technology known axial piston pump works.
  • control valve 33 When the control valve 33 is in an intermediate position between is fully open and fully closed there is a certain pressure build-up in the high pressure space 27a and 27b adjust when the associated pump piston 9 is in Delivery stroke is located. This pressure is about the first Transfer membrane 13 to the associated delivery chamber 17. As soon as the pressure in the delivery chamber 17 is greater than in High-pressure connection 25, the associated second opens Check valve 23 and it becomes a certain one Amount of fuel from the delivery chamber 17 in the High pressure connection 25 promoted. In this operating state the delivery rate of the high-pressure fuel pump 1 is larger than zero and less than the flow rate when the valve is closed Control valve 33. Depending on the position of the control valve 33 can the delivery rate can be set between 0 and 100%.
  • control valve 33 can also be used as a switching valve be carried out (not shown).
  • the flow control by opening and closing the Switch valve made. If the desired delivery rate was promoted by the pump elements 3, the Switch valve opened so that a pressure equalization between the pressure rooms 27a and 27b takes place and as a result no further fuel in the high pressure connection 25 is promoted. The larger the hydraulic cross sections the hydraulic connection 29 and the switching valve, the lower the loss, this type of flow control can be respectively. If the flow rate regulation by opening the Switch valve after reaching the desired flow rate takes place, the pressure surges in the low pressure range and in High-pressure area of high-pressure fuel pump 1 minimized. This flow rate regulation is particularly advantageous.
  • a second embodiment is one High-pressure fuel pump according to the invention in the form of a Cross section of axial piston pump greatly simplified shown.
  • three are at 120 ° Pump elements 3 offset from one another hinted at.
  • the high pressure connection and the Low pressure connection are not in this illustration shown, as well as the swashplate.
  • the formation of pressure room and Delivery space is based on the exemplary embodiment according to FIG. 1 directed.
  • Fig. 2 the hydraulic connection 29 is also between the pump elements 3 shown.
  • a control valve 33 is arranged, which with reference to FIG. 3, which is a section along the line A-B in Fig. 2nd represents, is explained in more detail below.
  • a Housing 31 of the high-pressure fuel pump 1 is a Hole 35 recessed.
  • a Rotary slide valve 37 is arranged, which via a shaft 39 in Rotation is offset.
  • the speed and phase of the Rotary valve 37 agree with the speed and the Phase position of the swash plate (not shown in FIG. 2 and 3) the axial piston pump.
  • the rotation of the shaft 39 is a groove 41 in the rotary valve 37 and a sliding block 43 from the shaft 39 to the rotary valve 37 transmitted.
  • the hydraulic connection 29 settles in Rotary valve 37 continues. Where the hydraulic connection 29 ends in the rotary valve, control grooves 45 are provided.
  • the hydraulic connections 29 in the housing 31 open into a control slot 47.
  • the control slots 47 open into the bore 35 in the housing 31.
  • the rotary valve 37 is in via an actuator 49 Longitudinal direction, indicated by the double arrows 51, displaceable. Depending on the coverage of control slots 47 and control grooves 45, the hydraulic connection 29 becomes more or less opened and thus the desired delivery rate set. This type of flow rate regulation was already explained in detail with reference to FIG. 1, and it to avoid repetitions on this Explanations referenced.
  • Control valves 33 are further embodiments of Control valves 33 shown.
  • the configuration of this Control valves 33 in an axial piston pump corresponds that of the embodiment of FIG. 3.
  • An actuator 49 actuates a longitudinal slide 53 in the direction of Double arrow 51.
  • a longitudinal slide 53 covers the control edge 55 of the Longitudinal slide 53 the control slots 47 completely, partially or not at all.
  • 4 is a position of the longitudinal slide 53, in which the Control slots 47 almost completely from the longitudinal slide 53 are covered. This means that only a small one Pressure equalization between the pressure rooms 27 (not shown) via the hydraulic connections 29 can be done.
  • FIG. 5 is another embodiment of a Control valve 33 shown, in which the hydraulic Connections 29 in the housing 31 directly into the bore 35 lead.
  • the longitudinal slide 53 In the longitudinal slide 53 is a circumferential Control groove 45 incorporated.
  • Position of the longitudinal slide 53 closes the hydraulic connections 29 so that no pressure equalization between the pump elements (not shown) can take place and thus promoted the full funding becomes. If the longitudinal slide 53 in Fig. 5 to the left is shifted, the control groove 45 allows one Connection of the hydraulic connections 29 so that a partial or full pressure equalization between the not shown pressure rooms takes place and thus the Flow rate is reduced.
  • the second membrane 15 can also be dispensed with become.
  • the hydraulic connection 29 the delivery spaces 17 of the pump elements 3 with each other connect.
  • the pressure equalization does not take place between the pressure rooms, but between the delivery rooms 17 instead, which affects the flow rate in the same way affects the high-pressure fuel pump according to the invention.
  • the advantage of this embodiment is the lower one Construction effort and space requirements.
  • FIG. 6 is a radial piston pump according to the state of the Technology shown schematically.
  • the three pump elements 3 are radial arranged to a drive shaft 9 and are from a eccentric section 57 of the drive shaft 9 driven.
  • This high-pressure fuel pump is on everyone Low pressure connection 19, a switching valve 59 is provided.
  • the switching valves 59 in the second, in Fig. 6 not Switch position shown are brought Switching valves 59 the function of the first check valves 21 (see Fig. 1), so that the pump elements 3 in the Promote high pressure connection 25.
  • the switching valves 59 are actuated, the Flow rate of the radial piston pump can be set.
  • the control of the switching valves 59 must be very done exactly and there are three complex switching valves 59 required.
  • FIG. 7 a first embodiment of a High-pressure fuel pump according to the invention, which as Radial piston pump is formed, shown.
  • a High-pressure fuel pump according to the invention which as Radial piston pump is formed, shown.
  • 7 connects the hydraulic Connection 29 to the delivery rooms 17a, 17b and 17c of three Pump elements 3, not shown Radial piston pump as described in FIG. 6 together.
  • FIG. 8 another embodiment is as Radial piston pump high-pressure fuel pump 1 shown.
  • About the switching valve 61 can be a hydraulic connection of the Conveying spaces 17a, 17b and 17c made with each other become. When this hydraulic connection is closed, the radial piston pump delivers the full flow. If the connection is fully open, a Zero funding.
  • the Switch valve 61 can between any desired flow rate 0% and 100% can be set.
  • FIG. 9 is an embodiment of a switching valve 61 shown in longitudinal section.
  • this switching valve 61 are the hydraulic connections 29 by a Longitudinal slide 53 closed or more or less open. Depending on the position of the longitudinal slide 53 can thus a more or less large pressure balance between the Delivery spaces 17a, 17b or 17c of the high-pressure fuel pump or the pressure chambers 27a or 27b (see FIG. 1).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP02027253A 2002-04-12 2002-12-06 Système de contrôle de capacité d'une pompe à combustible Withdrawn EP1353071A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10216205A DE10216205B4 (de) 2002-04-12 2002-04-12 Kraftstoffhochdruckpumpe mit Fördermengenregelung
DE10216205 2002-04-12

Publications (2)

Publication Number Publication Date
EP1353071A2 true EP1353071A2 (fr) 2003-10-15
EP1353071A3 EP1353071A3 (fr) 2004-11-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02027253A Withdrawn EP1353071A3 (fr) 2002-04-12 2002-12-06 Système de contrôle de capacité d'une pompe à combustible

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EP (1) EP1353071A3 (fr)
DE (1) DE10216205B4 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB837737A (en) * 1957-12-06 1960-06-15 Wm Butler & Co Bristol Ltd Improvements relating to hydraulically operated pumps
US3160104A (en) * 1960-11-08 1964-12-08 Rover Co Ltd Rotary fuel pump of the kind including cam-operated pistons
DE1811697A1 (de) * 1968-11-29 1970-06-11 Vni K I T I Vorrichtung zur Regulierung der Leistung einer Pumpe
DE3700997A1 (de) * 1986-02-01 1987-08-06 Zahnradfabrik Friedrichshafen Kolbenpumpe mit einer taumelscheibe oder einem exzenter
EP1101940A2 (fr) * 1999-11-18 2001-05-23 Siemens Automotive Corporation Régulation d'une pompe à carburant par immobilisation de pistons

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3927742A1 (de) * 1989-08-23 1991-02-28 Bosch Gmbh Robert Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
US5538403A (en) * 1994-05-06 1996-07-23 Cummins Engine Company, Inc. High pressure pump for fuel injection systems
DE19951999B4 (de) * 1999-10-28 2004-11-18 Siemens Ag Einspritzanlage für eine Brennkraftmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB837737A (en) * 1957-12-06 1960-06-15 Wm Butler & Co Bristol Ltd Improvements relating to hydraulically operated pumps
US3160104A (en) * 1960-11-08 1964-12-08 Rover Co Ltd Rotary fuel pump of the kind including cam-operated pistons
DE1811697A1 (de) * 1968-11-29 1970-06-11 Vni K I T I Vorrichtung zur Regulierung der Leistung einer Pumpe
DE3700997A1 (de) * 1986-02-01 1987-08-06 Zahnradfabrik Friedrichshafen Kolbenpumpe mit einer taumelscheibe oder einem exzenter
EP1101940A2 (fr) * 1999-11-18 2001-05-23 Siemens Automotive Corporation Régulation d'une pompe à carburant par immobilisation de pistons

Also Published As

Publication number Publication date
DE10216205B4 (de) 2007-04-05
EP1353071A3 (fr) 2004-11-03
DE10216205A1 (de) 2003-11-06

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