US20040156733A1 - High pressure feed pump - Google Patents

High pressure feed pump Download PDF

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Publication number
US20040156733A1
US20040156733A1 US10/771,574 US77157404A US2004156733A1 US 20040156733 A1 US20040156733 A1 US 20040156733A1 US 77157404 A US77157404 A US 77157404A US 2004156733 A1 US2004156733 A1 US 2004156733A1
Authority
US
United States
Prior art keywords
delivery piston
high pressure
spring element
delivery
feed pump
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.)
Abandoned
Application number
US10/771,574
Other languages
English (en)
Inventor
Fritz Spinnler
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.)
CRT Common Rail Tech AG
Original Assignee
CRT Common Rail Tech AG
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 CRT Common Rail Tech AG filed Critical CRT Common Rail Tech AG
Assigned to CRT COMMON RAIL TECHNOLOGIES AG reassignment CRT COMMON RAIL TECHNOLOGIES AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SPINNLER, FRITZ
Publication of US20040156733A1 publication Critical patent/US20040156733A1/en
Abandoned 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
    • 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
    • F04B1/0413—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
    • 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
    • F04B1/0426—Arrangements for pressing the pistons against the actuated cam; Arrangements for connecting the pistons to the actuated cam
    • 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
    • F04B1/0439—Supporting or guiding means for the pistons

Definitions

  • the present invention relates to a high pressure feed pump of the type which operates according to the reciprocating piston principle. More particularly, a pump of this type may be used to produce the injection pressure in fuel injection systems, for example common rail systems, for internal combustion engines.
  • a high pressure feed pump of the general type is disclosed in EP-A-1 058 001 and corresponding U.S. Pat. No. 6,205,980.
  • High pressure feed pumps of the described type have a high pressure cylinder or plunger cylinder and a cylindrical delivery piston or plunger piston which can be reciprocated therein, the volume of the delivery chamber within the high pressure cylinder being varied by the reciprocating movement of the plunger piston.
  • a filling stroke of the plunger piston it is possible to connect the delivery chamber to a reservoir chamber for a delivery medium via a filling valve, in order to fill the delivery chamber whose reciprocating volume is increasing with the delivery medium.
  • the pressure rises in the delivery chamber until a pressure valve opens and as a result connects the delivery chamber to a high pressure chamber, for example the common rail.
  • the plunger piston is driven by an eccentric drive which comprises an eccentric which is mounted on an eccentric shaft and on which a rolling ring is rotatably mounted.
  • the latter has a cambered circumferential surface to reduce its moment of inertia.
  • the delivery piston which is pretensioned in the direction toward the eccentric shaft, rests on the rolling ring with a plate-like extension which is provided at that end of said delivery piston.
  • the rolling ring rotates to and fro and changes its direction of rotation twice per revolution of the eccentric shaft.
  • a high pressure feed pump which includes a plate-like spring element positioned between the front end of the delivery piston and the rolling ring.
  • the rolling ring has a cambered circumferential surface, and the spring element rests firstly on the circumferential surface of the rolling ring via a contact surface, and secondly on the front end of the delivery piston via an annular surface.
  • FIG. 1 shows a transverse section through a high pressure feed pump according to the invention along the section line I-I of FIG. 2;
  • FIG. 2 shows the high pressure feed pump shown in FIG. 1 in a longitudinal section along the line II-II of FIG. 1;
  • FIG. 3 shows, partially in section, part of the high pressure feed pump shown in FIGS. 1 and 2 having a delivery piston which is of concave shape at the front end and rests on a bucket shaped tappet which at the other end interacts with a rolling ring of a drive shaft;
  • FIG. 4 shows, in the same representation as FIG. 3, a further embodiment of the high pressure feed pump according to the invention having an adapter head which is movably mounted on a shaft of the delivery piston;
  • FIG. 5 shows a section along the line V-V of the embodiment shown in FIG. 4.
  • FIG. 6 shows, in the same representation as FIG. 3, a further embodiment, in which the front end of the delivery piston is of planar design and the bucket shaped tappet has a concave recess.
  • FIGS. 1 and 2 show a transverse section and a longitudinal section through a high pressure feed pump having a main housing 10 , which has a radial chamber into which a high pressure cylinder 12 (also called a plunger cylinder) is positioned.
  • a delivery piston 14 (also called a plunger piston) can move to and fro in the direction of the longitudinal axis 14 ′.
  • the high pressure cylinder 12 is clamped with a flange-like extension between the main housing 10 and a valve housing 16 .
  • the valve housing 16 is joined to the housing 10 by means of threaded bolts 17 .
  • An inlet valve 18 and an outlet valve 20 are provided in the valve housing 16 .
  • the inlet valve 18 opens and closes a passage 22 to a storage container for the medium to be delivered, and the outlet valve 20 opens and closes a passage 24 to a high pressure container.
  • fuel such as diesel or gasoline is situated in the storage container, and the high pressure container is, for example, a common rail.
  • an eccentric drive 26 for driving the delivery piston 14 is arranged in the housing 10 of the high pressure feed pump.
  • the eccentric drive 26 has a drive shaft 28 which is continuously driven in the direction of the arrow and is mounted in a generally known manner in the housing 10 which includes a cover 32 which closes the latter. Bearings (not shown) may be provided such that the drive shaft 28 can freely rotate about a rotational axis 30 .
  • the drive shaft 28 bears an eccentric journal 36 which is arranged eccentrically with regard to the rotational axis 30 of the drive shaft 28 and whose center axis 38 runs parallel to the rotational axis 30 .
  • a rolling ring 40 is mounted on the eccentric journal 36 in a rotatable manner with respect to the eccentric journal 36 .
  • the radially outer circumferential surface 42 of the rolling ring 40 is cambered, that is to say is of convex design, as best seen in FIG. 2.
  • a through bore 44 in the shape of a circular cylinder, is formed in the high pressure cylinder 12 , and the bore 44 is coaxial with the axis 14 ′, which preferably extends perpendicular to the rotational axis 30 of the draft shaft.
  • the delivery piston 14 is displaceably guided in the bore with a sliding seal. Its end region facing the drive shaft 28 engages in a bucket shaped tappet 46 , on whose base 48 it rests with the front end 50 of a mushroom shaped or plate shaped extension 52 .
  • the base 48 of the bucket shaped tappet 46 sits on the rolling ring 40 at the other side.
  • the reference numeral 54 denotes the point of contact or contact area between the rolling ring 40 and the base 48 of the bucket shaped tappet 46 .
  • the delivery piston 14 is pretensioned in the direction toward the rolling ring 40 by means of a compression spring 56 which is supported at one end on the high pressure cylinder 12 and at the other end on the extension 52 .
  • the outer circumferential wall 58 of the bucket shaped tappet 46 is guided in a sliding manner in a radial chamber formed in the housing 10 for sliding movement in the longitudinal direction and hence in the direction of movement of the delivery piston 14 .
  • the transverse forces which act on the bucket shaped tappet 46 from the drive shaft 28 and the rolling ring 40 are absorbed by the bucket shaped tappet 46 and are not transmitted to the delivery piston 14 , or only to a very small degree.
  • the delivery piston 14 In order to compress and deliver the delivery medium, the delivery piston 14 is reciprocated up and down by the eccentric drive 26 and the compression spring 56 .
  • the delivery chamber 60 When the delivery piston 14 moves downward during a filling stroke, the delivery chamber 60 is filled with the delivery medium via the inlet valve 18 .
  • the pressure in the delivery chamber 60 rises with the inlet valve 18 closed, until the outlet valve 20 opens and as a result connects the delivery chamber 60 to the high pressure container (e.g. a common rail). In the process, the delivery medium is delivered into the high pressure container.
  • the high pressure container e.g. a common rail
  • FIG. 3 shows the delivery piston 14 , the compression spring 56 , the bucket shaped tappet 46 , the rolling ring 40 and part of the drive shaft 28 , which can be driven in the direction of the arrow, having the eccentric journal 36 .
  • the bucket shaped tappet 46 is preferably made from hardened roller bearing steel.
  • the plate shaped base 48 of the bucket shaped tappet 46 which is flat in the unloaded state, has spring properties and serves as a spring element 62 in its interaction on one side with the cambered circumferential surface 42 of the rolling ring 40 and on the other side with the concavely designed front end 50 of the delivery piston 14 .
  • the depression 64 in the end of the delivery piston 14 can be shaped, for example, as a spherical cap or part of the circumferential surface of a torus.
  • the front end 50 of the delivery piston 14 has a flat annular surface 66 , with which it rests on the base 48 in the unloaded or lightly loaded state and which can have the shape of a circular ring, oval or other shape depending on the shape of the depression 64 .
  • the longitudinal axis 14 ′ of the delivery piston 14 should run centrally with respect to the depression 64 or annular surface 66 and with respect to the bucket shaped tappet 46 .
  • the axis 14 ′ preferably runs in a plane extending at right angles to the rotational axis 30 of the drive shaft 28 , said plane extending centrally through the contact area 54 .
  • the base 48 acting as a spring element 62 , of the bucket shaped tappet 46 is deformed into the depression 64 as a function of the loading of the delivery piston 14 in such a way that, when the load becomes greater, firstly the contact area 54 between the base 48 and the rolling ring 40 and secondly the area over which the base 48 rests on the delivery piston 14 are enlarged.
  • the base 48 is preferably dimensioned in such a way that its entire area rests in the depression 64 on the delivery piston 14 in the case of a specific load.
  • the delivery piston 14 shown in FIGS. 4 and 5 has a shaft 68 , on whose end region, which is shaped like a hemisphere and faces the rolling ring 40 , sits an adapter head 70 of substantially circular cylindrical shape.
  • the front end 50 which interacts with the base 48 of the bucket shaped tappet 46 , of the head adapter 70 is of the same design as that in the case of the delivery piston 14 according to FIG. 3.
  • a recess 72 of the adapter head 70 for accommodating the end region of this side of the shaft 68 is shaped to be diametrically opposed to said end region and has a peripheral groove 74 in a cylindrical outer part adjoining the hemispherical surface.
  • the shaft 68 is correspondingly provided with a circumferential groove 76 .
  • a rectilinear through hole 78 runs through the adapter head 70 , whose axis is tangent to the circular center line of the toroidal chamber delimited by the groove 74 and the circumferential groove 76 .
  • a section of a securing element formed from spring steel wire 80 extends through the through hole 78 , and a further section of said securing element extends around the adapter head 70 in order to fasten it.
  • the adapter head 70 is mounted on the shaft 68 in the manner of a sphere with limited mobility. This makes it possible for exclusively axial forces and no bending forces to act on the delivery piston 14 .
  • the compression spring 56 is supported on a flange ring 82 which engages around two half flanges 84 and is for its part supported on the latter.
  • a bead 86 of the half flanges 84 engages in a circumferential groove of the shaft 68 and the half flanges 84 are attached in this way to the shaft 68 in the axial direction.
  • FIG. 6 of the high pressure feed pump according to the invention is very similar to that according to FIG. 3, the front end 50 of the delivery piston 14 being of flat design and the base 48 of the bucket shaped tappet 46 being of concave shape as a result of a recess 64 ′ on the side facing the delivery piston 14 .
  • the delivery piston 14 rests in the unloaded and lightly loaded state with an annular surface 66 on the base 48 , acting as a spring element 62 , of the bucket shaped tappet 46 .
  • the method of operation is the same as described further above in conjunction with the other embodiments.
  • the delivery piston 14 can be of the same design as shown in FIG. 3 or 4 .
  • the transition between the annular surface 66 and the depression 64 ′ is itself preferably shaped in a manner corresponding to the spring characteristic of the spring element 62 , such that the area with which the spring element rests on the delivery piston is continuously enlarged as the load rises.
  • the depression 64 ′ can be matched to the camber of the rolling ring 40 in such a way that, when at least approximately the whole area of the spring element 62 rests in the depression 64 ′, the spring element 62 also rests on the rolling ring 40 across at least approximately the whole width of the latter.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US10/771,574 2001-08-08 2004-02-04 High pressure feed pump Abandoned US20040156733A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CH14602001 2001-08-08
CH20011460/01 2001-08-08
PCT/CH2002/000374 WO2003014569A1 (de) 2001-08-08 2002-07-09 Hochdruckförderpumpe

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/CH2002/000374 Continuation WO2003014569A1 (de) 2001-08-08 2002-07-09 Hochdruckförderpumpe

Publications (1)

Publication Number Publication Date
US20040156733A1 true US20040156733A1 (en) 2004-08-12

Family

ID=4565497

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/771,574 Abandoned US20040156733A1 (en) 2001-08-08 2004-02-04 High pressure feed pump

Country Status (6)

Country Link
US (1) US20040156733A1 (de)
EP (1) EP1415092A1 (de)
JP (1) JP2004537005A (de)
KR (1) KR20040035730A (de)
CN (1) CN1539060A (de)
WO (1) WO2003014569A1 (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060062677A1 (en) * 2003-02-11 2006-03-23 Marco Ganser High pressure pump
US20090071446A1 (en) * 2005-06-08 2009-03-19 Sakae Sato Fuel supply pump and tappet structure body
US20090191077A1 (en) * 2008-01-29 2009-07-30 Denso Corporation Pump
US20110023704A1 (en) * 2008-03-26 2011-02-03 Friedrich Boecking Pump, in particular high-pressure fuel pump
CN102472257A (zh) * 2009-06-29 2012-05-23 罗伯特·博世有限公司 高压泵
US20130177462A1 (en) * 2010-07-09 2013-07-11 Grundfos Management A/S Dosing pump arrangement
US20200158086A1 (en) * 2017-06-09 2020-05-21 Delft Offshore Turbine B.V. Wind turbine generator with hydraulic pump

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10344459B4 (de) * 2003-09-25 2012-06-14 Robert Bosch Gmbh Kolbenpumpe, insbesondere Hochdruck-Kolbenpumpe
ATE439517T1 (de) * 2005-03-24 2009-08-15 Delphi Tech Inc Kraftstoffpumpe
DE102005056683B3 (de) * 2005-11-28 2007-05-03 Industriehansa Consulting & Engineering Gmbh Verbesserte Verdrängungseinheit für eine Hochdruckpumpe
DE102006043187B3 (de) * 2006-09-14 2008-04-03 Siemens Ag Fluidpumpe, insbesondere Hochdruck-Kraftstoffpumpe für Einspritzsysteme von Brennkraftmaschinen
DE102006045897B4 (de) * 2006-09-28 2008-09-11 Continental Automotive Gmbh Radialkolbenpumpe zur Kraftstoffhochdruckversorgung
DE102008008438A1 (de) * 2008-02-11 2009-08-13 Continental Automotive Gmbh Hochdruckpumpe
DE102010042484A1 (de) * 2010-10-15 2012-04-19 Robert Bosch Gmbh Hochdruckpumpe für eine Kraftstoffeinspritzvorrichtung
CN103047100A (zh) * 2013-01-10 2013-04-17 无锡开普机械有限公司 具有凸轮轴轴套的转子泵
CN105862979A (zh) * 2016-05-12 2016-08-17 张萍 一种高效的智能化空气制水机

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2079821A (en) * 1935-03-21 1937-05-11 Timken Roller Bearing Co Fuel injection pump
US2126985A (en) * 1935-02-01 1938-08-16 Timken Roller Bearing Co Fuel injection pump
US3272088A (en) * 1964-06-17 1966-09-13 Westinghouse Air Brake Co Conversion brake cylinder
US3320902A (en) * 1963-05-09 1967-05-23 Paschke Hanns-Dieter Rotary piston machine
US6077056A (en) * 1997-02-12 2000-06-20 Robert Bosch Gmbh Reciprocating pump
US6205980B1 (en) * 1999-05-31 2001-03-27 Sig Schweizerische Industrie-Gesellschaft High-pressure delivery pump
US6350107B1 (en) * 1998-04-01 2002-02-26 Robert Bosch, Gmbh Radial piston pump for supplying a high fuel pressure

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3505176C1 (de) * 1985-02-15 1986-04-24 Hauhinco Maschinenfabrik G. Hausherr, Jochums Gmbh & Co Kg, 4300 Essen Radialkolbenpumpe für hydraulische Medien
DE19956092A1 (de) * 1999-11-22 2000-10-26 Siemens Ag Kolbenpumpe, insbesondere Hochdruck-Radialkolbenpumpe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2126985A (en) * 1935-02-01 1938-08-16 Timken Roller Bearing Co Fuel injection pump
US2079821A (en) * 1935-03-21 1937-05-11 Timken Roller Bearing Co Fuel injection pump
US3320902A (en) * 1963-05-09 1967-05-23 Paschke Hanns-Dieter Rotary piston machine
US3272088A (en) * 1964-06-17 1966-09-13 Westinghouse Air Brake Co Conversion brake cylinder
US6077056A (en) * 1997-02-12 2000-06-20 Robert Bosch Gmbh Reciprocating pump
US6350107B1 (en) * 1998-04-01 2002-02-26 Robert Bosch, Gmbh Radial piston pump for supplying a high fuel pressure
US6205980B1 (en) * 1999-05-31 2001-03-27 Sig Schweizerische Industrie-Gesellschaft High-pressure delivery pump

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060062677A1 (en) * 2003-02-11 2006-03-23 Marco Ganser High pressure pump
US7108491B2 (en) 2003-02-11 2006-09-19 Ganser-Hydromag Ag High pressure pump
US20060275164A1 (en) * 2003-02-11 2006-12-07 Marco Ganser High pressure pump
US20090071446A1 (en) * 2005-06-08 2009-03-19 Sakae Sato Fuel supply pump and tappet structure body
US7661413B2 (en) 2005-06-08 2010-02-16 Bosch Corporation Fuel supply pump and tappet structure body
US20090191077A1 (en) * 2008-01-29 2009-07-30 Denso Corporation Pump
US20110023704A1 (en) * 2008-03-26 2011-02-03 Friedrich Boecking Pump, in particular high-pressure fuel pump
CN102472257A (zh) * 2009-06-29 2012-05-23 罗伯特·博世有限公司 高压泵
US20130177462A1 (en) * 2010-07-09 2013-07-11 Grundfos Management A/S Dosing pump arrangement
US9388800B2 (en) * 2010-07-09 2016-07-12 Grundfos Management A/S Dosing pump arrangement
US20200158086A1 (en) * 2017-06-09 2020-05-21 Delft Offshore Turbine B.V. Wind turbine generator with hydraulic pump

Also Published As

Publication number Publication date
EP1415092A1 (de) 2004-05-06
WO2003014569A1 (de) 2003-02-20
CN1539060A (zh) 2004-10-20
JP2004537005A (ja) 2004-12-09
KR20040035730A (ko) 2004-04-29

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Legal Events

Date Code Title Description
AS Assignment

Owner name: CRT COMMON RAIL TECHNOLOGIES AG, SWITZERLAND

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SPINNLER, FRITZ;REEL/FRAME:014967/0277

Effective date: 20040120

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION