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WO2013037543A1 - Pompe, notamment pompe à carburant haute pression - Google Patents

Pompe, notamment pompe à carburant haute pression Download PDF

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Publication number
WO2013037543A1
WO2013037543A1 PCT/EP2012/064077 EP2012064077W WO2013037543A1 WO 2013037543 A1 WO2013037543 A1 WO 2013037543A1 EP 2012064077 W EP2012064077 W EP 2012064077W WO 2013037543 A1 WO2013037543 A1 WO 2013037543A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
housing part
pump housing
valve
holding element
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.)
Ceased
Application number
PCT/EP2012/064077
Other languages
German (de)
English (en)
Inventor
Friedrich Boecking
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 WO2013037543A1 publication Critical patent/WO2013037543A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F02M59/02—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
    • F02M59/10—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 the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F04B1/0408—Pistons
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/803—Fuel injection apparatus manufacture, repair or assembly using clamp elements and fastening means; e.g. bolts or screws

Definitions

  • the invention relates to a pump, in particular high-pressure fuel pump, according to the preamble of claim 1.
  • Such a pump in the form of a high-pressure fuel pump is known from DE 10 2008 000 705 AI.
  • This pump has a multi-part pump housing and at least one pump element.
  • the pump element has a pump piston which is driven at least indirectly by a drive shaft in a lifting movement.
  • the pump piston is displaceably guided in a cylinder bore of a first pump housing part and delimits a pump working space in the cylinder bore.
  • the pump working space can be connected to an inlet via an inlet valve and to an outlet via an outlet valve.
  • the first pump housing part is connected to a second pump housing part, in which at least partially extends the inlet and in which the drive shaft may be mounted.
  • the high-pressure region of the pump is substantially concentrated on the first pump housing part, which is made of correspondingly high-pressure-resistant material.
  • the second pump housing part is not loaded with high pressure and can be made of material with correspondingly lower strength.
  • the inlet valve and the outlet valve are arranged in the first pump housing part, which is complicated to receive the valves and thus is correspondingly expensive and expensive to manufacture. Disclosure of the invention
  • the pump according to the invention with the features of claim 1 has the advantage that the first pump housing part can be made simple and inexpensive to produce, since this does not need to accommodate the inlet valve.
  • the embodiment according to claim 2 allows a simple design and manufacture of the retaining element.
  • the embodiment according to claim 3 allows a simple design and Herl s position of the first pump housing part.
  • the embodiment according to claim 4 enables a simple reception of the inlet valve in the holding element.
  • the embodiment according to claims 6 and 7 enables a simple arrangement and sealing between the inlet valve and the first pump housing part. Due to the construction according to claim 6, the connection of the inlet valve 20 to the inlet is made in a simple manner.
  • the embodiment according to claim 8 allows a favorable arrangement of the exhaust valve.
  • FIG. 1 shows a pump in a longitudinal section
  • FIG. 2 shows a detail of the pump designated II in FIG. 1 in an enlarged view
  • FIG. 3 shows the detail II in a view in the direction of arrow III in FIG.
  • FIGS. 1 to 3 show a pump which is in particular a high-pressure fuel pump for a fuel injection device of an internal combustion engine.
  • the pump has at least one pump element 10, which is again to a pump piston 12 which is at least indirectly driven by a drive shaft 14 in a lifting movement in at least approximately radial direction with respect to the axis of rotation 15 of the drive shaft 14.
  • the drive shaft 14 may be part of the pump or alternatively may also be provided that the pump does not have its own drive shaft and the drive shaft 14 is part of the internal combustion engine.
  • the drive shaft 14 may be, for example, a shaft of the internal combustion engine through which the gas exchange valves of the internal combustion engine are actuated.
  • the drive shaft 14 may have a cam 16 or eccentric for driving the pump piston 12.
  • the pump has a multi-part pump housing.
  • the pump piston 12 is tightly guided in a cylinder bore 20 of a first housing part 22 of the pump wherein the first housing part 22 is referred to below as the cylinder head.
  • the pump piston 12 in the cylinder bore 20 defines a pump working space 24.
  • the pump working space 24 has an inlet valve 26, which is for example an inlet check valve opening into the pump working space 24, a connection to an inlet leading, for example, from a feed pump 28, over which the pump working chamber 24 at the radially inwardly directed to the rotational axis 15 of the drive shaft 14 suction stroke of the pump piston 12 is filled with fuel.
  • the pump working chamber 24 also has an outlet valve 30, which is for example an outlet check valve opening out of the pump working chamber 24, a connection to a drain 32, which leads, for example, to a high-pressure fuel accumulator 34 and via the radially outward from the axis of rotation 15 of the drive shaft 14 away pumping stroke of the pump piston 12 fuel is displaced from the pump working chamber 24.
  • an outlet valve 30 is for example an outlet check valve opening out of the pump working chamber 24
  • a connection to a drain 32 which leads, for example, to a high-pressure fuel accumulator 34 and via the radially outward from the axis of rotation 15 of the drive shaft 14 away pumping stroke of the pump piston 12 fuel is displaced from the pump working chamber 24.
  • the pump piston 12 is supported indirectly via a roller tappet 36 on the cam 16 of the drive shaft 14.
  • a roller 37 is rotatably mounted, which runs on the cam 16.
  • the pump piston 12 is connected to the roller tappet 36 in a manner not shown.
  • the roller tappet 36 and with this the pump piston 12 is acted upon by a spring 38 to the cam 16 of the drive shaft 14, so that the roller 37 constantly, so even during the suction stroke of the pump piston 12, remains in contact with the cam 16.
  • the housing of the pump has a second housing part 40, in which the drive shaft 14 can be rotatably supported via one or more bearings.
  • the inlet 28 can run through the housing part 40, in particular through an interior 42 of the housing part 40, in which the cam 16 of the drive shaft 14 is arranged, and through holes 43 or channels in the housing part 40th
  • the cylinder head 22 is substantially cylindrical, in particular nikzylin- derförmig formed and protrudes with an end portion in which the cylinder bore
  • the cylinder bore 20 is formed, in which the pump piston 12 is arranged, through an opening 44 of the second housing part 40 in the interior 42 into it.
  • the cylinder bore 20 opposite end portion of the cylinder head 22 is disposed outside of the second housing part 40.
  • a circumferential collar 46 is formed on the latter, whose diameter is greater than the diameter of the opening 44 of the second housing part 40.
  • the cylinder head 22 lies with its collar 46 on the outside of the second Housing part 40 at the edge of the opening 44, whereby the position of the cylinder head 22 in its longitudinal direction to the second housing part 40 is fixed.
  • transverse bore 48 which opens on the outer surface of the cylinder head 22 in its outside of the second housing part 40 arranged region.
  • the transverse bore 48 preferably runs at least approximately perpendicularly to the cylinder bore 20 and has a smaller diameter than the cylinder bore 20.
  • the cylinder head 22 has a flattening 49 in its outer jacket, which is at least approximately perpendicular to the longitudinal axis the transverse bore 48 extends.
  • annular groove 50 is arranged in the circular cylindrical outer surface of the cylinder head 22.
  • cylinder bore 20 also performs another with this at least approximately coaxial longitudinal bore 52 from the second housing part 40 projecting end of the cylinder head 22, wherein the longitudinal bore 52 in its discharging from the cylinder bore 20 end portion has a smaller diameter than the cylinder bore 20 and the End of cylinder head 22 toward an enlarged diameter.
  • the longitudinal bore 52 can also be offset and extend at least approximately parallel to the cylinder bore 20.
  • the longitudinal bore 52 leads to the outlet valve 30, which will be described in more detail below.
  • the cylinder head 22 is fastened to the second housing part 40 by means of a flange-like retaining element 54.
  • the holding element 54 surrounds the region of the cylinder head 22 arranged outside the second housing part 40 in a ring shape and lies on the outside of the housing part 40.
  • the holding element 54 has, for example, an approximately circular cross-section, but may also have a different cross-sectional shape, for example a polygonal or oval cross-sectional shape.
  • the holding element 54 has an opening 55 whose diameter is only slightly larger than the diameter of the region of the cylinder head 22 arranged outside the second housing part 40.
  • the opening 55 is enlarged in diameter corresponding to the diameter of the housing Collar 46 of the cylinder head 22, so that on the holding element 54 a housing part 40 facing annular shoulder 56 is formed.
  • the collar 46 of the cylinder head 22 is disposed in the region of the larger diameter opening 55 and is pressed by the annular shoulder 56 against the outside of the housing part 40.
  • the holding element 54 is fastened by means of one or more screws 57 on the housing part 40 and also holds the cylinder head 22 on the housing part 40th
  • the holding element 54 has in its circumference a bore 58 which extends at least approximately coaxially with the transverse bore 48 of the cylinder head 22.
  • the bore 58 has a larger diameter than the transverse bore 48 and is provided in its opening on the outer surface of the retaining element 54 end portion with an internal thread 59.
  • the inlet valve 26 is arranged, which is formed for example as an inlet check valve.
  • the inlet valve 26 has a valve housing 60, which is formed substantially circular cylindrical, whose outer diameter is only slightly smaller than the diameter of the bore 58.
  • the valve housing 60 has a longitudinally extending through bore 61 and at least one, preferably a plurality of distributed over the circumference transverse bores 62, on the one hand on the outer surface of the valve housing 60 and on the other hand in the through hole 61 open.
  • a peripheral annular groove 63 is provided in the outer casing of the valve housing 60.
  • the inlet valve 26 has a piston-shaped valve member 64, which has a shaft 66 displaceably guided in a section of the through-bore 61 and a head 67 which is larger in diameter than the shaft 66 and which extends from the through-bore 61 on the side of the valve housing 60 facing the cylinder head 22 protrudes.
  • a sealing surface 68 is formed, with which the valve member 64 cooperates with a valve housing 60 arranged on the valve seat 69.
  • the shaft 66 of the valve member 64 protrudes on the side facing away from the cylinder head 22 from the through hole 61 of the valve housing 60 and at this engages a prestressed closing spring 71 via a spring plate 70. By the closing spring 71, the valve member 64 is acted upon with its sealing surface 68 to the valve seat 69 out.
  • an inlet bore 72 is provided, which opens on the one hand into the bore 58 in the region of the annular groove 63 of the valve housing 60 and on the other hand on the second housing part 40 facing end face of the holding element 54.
  • the inlet bore 72 may, for example, as shown in Figure 2 extend obliquely to the longitudinal axis of the bore 58 and connects the annular groove 63 of the valve housing 60 with the second housing part 40 extending bore 43, which is also part of the inlet 28.
  • a sealing element 73 may be arranged, for example in the form of an elastic sealing ring.
  • a sealing element 74 for example in the form of an elastic sealing ring, in particular an O-ring, arranged, through which the opening 55 of the holding member 54 is sealed to the outside.
  • a seal against the pressure prevailing in the pump working chamber 24 high pressure is required between the valve housing 60 of the intake valve 26 and the cylinder head 22.
  • This sealing takes place by means of a valve housing 60 on its side facing the flattening 49 of the cylinder head 22 end face. Dete sealing edge 76, which comes to the flattening 49 to the plant.
  • the valve housing 60 is pressed by means of a screwed into the internal thread 59 of the bore 58 of the support member 54 clamping screw 78 with its sealing edge 76 against the flattening 49.
  • the clamping screw 78 has a recess 79 in which the protruding from the valve housing 60 shaft 66 and the closing spring 71 are arranged.
  • a sealing element 80 for example in the form of an elastic sealing ring, can be arranged between the clamping screw 78 and the bore 58 of the holding element 54.
  • the holding element 54 has on its outer surface a bore 58 surrounding the flattening on which the head of the clamping screw 78 rests.
  • the outlet valve 30 is designed as a check valve and has a in a relation to the opening into the pump working chamber 24 part 152 of the longitudinal bore 52 enlarged in diameter guide portion 252 of the longitudinal bore 52 slidably guided, piston-shaped valve member 82.
  • the valve member 82 has at its end facing the pump working chamber 24 a sealing surface 83, with which it cooperates with a arranged in the longitudinal bore 52 valve seat 84.
  • the valve seat 84 is formed at the transition from the opening into the pump working chamber 24 Part 152 of the longitudinal bore 52 to the guide portion 252 and, for example, approximately conical.
  • the sealing surface 83 of the valve member 82 may also be approximately conical or, for example, spherical segment-shaped.
  • the valve member 82 has in its outer shell a plurality of longitudinally extending grooves 85 which form fürströmquerritte through which at its raised with its sealing surface 83 from the valve seat 84 valve member 82 fuel can flow.
  • the stroke movement of the valve member 82 in the opening direction is limited by a Hubanschlagelement 86, which is arranged on the pump working chamber 24 side facing away from the valve member 82 in the longitudinal bore 52.
  • the Hubanschlagelement 86 has distributed over its circumference a plurality of openings 87 which form flow cross sections and which are aligned with the grooves 85 of the valve member 82.
  • the outwardly facing end portion of the longitudinal bore 52 of the cylinder head 22 is provided with an internal thread 88 into which a connecting piece 89 is screwed, by which the Hubanschlagelement 86 is fixed in the longitudinal bore 52.
  • a high-pressure accumulator 34 leading hydraulic line can be connected.
  • the intake valve 26 described above is designed as an inlet check valve, which opens due to the pressure difference between the inlet 28 and the pump working chamber 24 during the suction stroke of the pump piston 12 and closes at the delivery stroke.
  • the intake valve 26 described above is designed as an inlet check valve, which opens due to the pressure difference between the inlet 28 and the pump working chamber 24 during the suction stroke of the pump piston 12 and closes at the delivery stroke.
  • the intake valve 26 described above is designed as an inlet check valve, which opens due to the pressure difference between the inlet 28 and the pump working chamber 24 during the suction stroke of the pump piston 12 and closes at the delivery stroke.
  • the intake valve 26 described above is designed as an inlet check valve, which opens due
  • Inlet valve 26 can be actively opened and / or closed by an actuator, in particular an electric actuator.
  • an actuator in particular an electric actuator.
  • the inlet valve 26 does not have its own valve housing and the retaining element 54 forms the housing for the inlet valve 26 and the valve member 64 in one

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe comprenant un carter (22,40) en plusieurs parties, et au moins un élément de pompe (10) qui présente un piston (12) entraîné dans un mouvement de course au moins indirectement par un arbre d'entraînement (14). Le piston (12) est guidé mobile dans un alésage cylindrique (20) d'une première partie (22) du carter de pompe et délimite un espace de travail (24) de pompe dans l'alésage cylindrique (20). L'espace de travail (24) de pompe peut être relié à une arrivée d'alimentation (28) par l'intermédiaire d'une soupape d'admission (26) et à une sortie d'évacuation (32) par l'intermédiaire d'une soupape d'évacuation (30). La première partie (22) de carter de pompe est reliée au moins indirectement à une deuxième partie (40) de carter de pompe. La première partie (22) de carter de pompe est fixée à la deuxième partie (40) de carter de pompe par l'intermédiaire d'un élément de retenue (54) appliqué sur ladite première partie, et la soupape d'admission (26) est disposée dans l'élément de retenue (54) perpendiculairement à l'axe de l'alésage cylindrique.
PCT/EP2012/064077 2011-09-15 2012-07-18 Pompe, notamment pompe à carburant haute pression Ceased WO2013037543A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011082733.1 2011-09-15
DE201110082733 DE102011082733A1 (de) 2011-09-15 2011-09-15 Pumpe, insbesondere Kraftstoffhochdruckpumpe

Publications (1)

Publication Number Publication Date
WO2013037543A1 true WO2013037543A1 (fr) 2013-03-21

Family

ID=46514397

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/064077 Ceased WO2013037543A1 (fr) 2011-09-15 2012-07-18 Pompe, notamment pompe à carburant haute pression

Country Status (2)

Country Link
DE (1) DE102011082733A1 (fr)
WO (1) WO2013037543A1 (fr)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999002861A1 (fr) * 1997-07-11 1999-01-21 Robert Bosch Gmbh Soupape d'admission pour pompe a pistons radiaux pour alimentation haute pression en carburant
EP1058001A1 (fr) * 1999-05-31 2000-12-06 SIG Schweizerische Industrie-Gesellschaft Pompe d'alimentation haute pression
WO2005052357A1 (fr) * 2003-11-28 2005-06-09 Ganser-Hydromag Ag Pompe d'alimentation haute pression destinee a des moteurs a combustion interne
DE102008000705A1 (de) 2008-03-17 2009-09-24 Robert Bosch Gmbh Hochdruckpumpe
DE102009027273A1 (de) * 2009-06-29 2010-12-30 Robert Bosch Gmbh Hochdruckpumpe
WO2011098320A1 (fr) * 2010-02-12 2011-08-18 Robert Bosch Gmbh Culasse pour pompe à carburant haute pression

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999002861A1 (fr) * 1997-07-11 1999-01-21 Robert Bosch Gmbh Soupape d'admission pour pompe a pistons radiaux pour alimentation haute pression en carburant
EP1058001A1 (fr) * 1999-05-31 2000-12-06 SIG Schweizerische Industrie-Gesellschaft Pompe d'alimentation haute pression
WO2005052357A1 (fr) * 2003-11-28 2005-06-09 Ganser-Hydromag Ag Pompe d'alimentation haute pression destinee a des moteurs a combustion interne
DE102008000705A1 (de) 2008-03-17 2009-09-24 Robert Bosch Gmbh Hochdruckpumpe
DE102009027273A1 (de) * 2009-06-29 2010-12-30 Robert Bosch Gmbh Hochdruckpumpe
WO2011098320A1 (fr) * 2010-02-12 2011-08-18 Robert Bosch Gmbh Culasse pour pompe à carburant haute pression

Also Published As

Publication number Publication date
DE102011082733A1 (de) 2013-03-21

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