WO2017055103A1 - Pompe haute pression - Google Patents

Pompe haute pression Download PDF

Info

Publication number
WO2017055103A1
WO2017055103A1 PCT/EP2016/071898 EP2016071898W WO2017055103A1 WO 2017055103 A1 WO2017055103 A1 WO 2017055103A1 EP 2016071898 W EP2016071898 W EP 2016071898W WO 2017055103 A1 WO2017055103 A1 WO 2017055103A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
pin
axis
roller shoe
plunger
Prior art date
Application number
PCT/EP2016/071898
Other languages
German (de)
English (en)
Inventor
Uwe Nigrin
Original Assignee
Continental Automotive 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 Continental Automotive Gmbh filed Critical Continental Automotive Gmbh
Priority to KR1020187008884A priority Critical patent/KR20180048853A/ko
Priority to CN201680057087.3A priority patent/CN108026903B/zh
Publication of WO2017055103A1 publication Critical patent/WO2017055103A1/fr

Links

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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections

Definitions

  • the invention relates to a high-pressure pump according to patent claim 1.
  • a high-pressure pump for conveying a fluid with a pump housing wherein in the pump housing a rotatably mounted drive shaft is provided.
  • the high-pressure pump has a pump piston, which is driven by a roller shoe and a roller through the drive shaft ⁇ . Furthermore, a plunger is provided on which the roller shoe is attached.
  • the object of the invention is to provide an improved high-pressure pump.
  • the object of the invention is achieved by the high pressure pump according to claim 1.
  • An advantage of the described high-pressure pump is that it is ensured by simple means that the roller shoe and thus the roller does not rotate with respect to a predetermined position with respect to the axis of rotation of the drive shaft. In this way it is achieved that the roller shoe is aligned substantially parallel to the axis of rotation of the drive shaft.
  • a fastening pin is provided, wherein the fastening pin rotatably connects the roller shoe with the pump housing with respect to the pump axis.
  • the fastening pin is directed in particular at a predetermined angle to the pump axis, in particular perpendicular to the pump axis ⁇ .
  • the fastening pin represents a pin-like Ext ⁇ rabauteil.
  • the fastening pin is secured to a first end of the roller shoe, its mountings is supply pin ⁇ passed through an opening of the plunger, and wherein a second end of the fixing pin is arranged in a groove of the pump housing.
  • the groove extends parallel to the pump axis so that the groove secures the second end of the mounting pin against rotation with respect to the pump axis.
  • the attachment pin may have an elongate pin head at the second end that is aligned along the groove. In this way, an improved lateral guidance is achieved.
  • the first attachment pin is attached to the roller shoe with a first end.
  • a second end of the attachment pin is attached to the plunger.
  • a second fastening pin is attached to a first end of the plunger, wherein a second end of the second attachment ⁇ pin is arranged in a groove of the pump housing.
  • a second groove on the plunger is formed from ⁇ , wherein the second end of the first fastening pin is disposed in the second groove. The second groove can be guided to a lower end of the plunger, so that a simple mounting of the roller shoe with a pre-assembled first fastening pin by insertion into the plunger is possible.
  • the first end of a fastening pin with a press fit in a recess of the Roller shoe or mounted in a recess of the plunger.
  • 1 is a schematic cross section through a high-pressure pump
  • FIG. 2 is a more detailed view of a partial section of the high-pressure pump of FIG. 1,
  • FIG. 4 shows a cross section perpendicular to the pump axis in the region of a second fastening pin
  • FIG. 5 shows a partial cross section perpendicular to the pump axis through a further embodiment of a high pressure pump
  • FIG. 6 shows a partial cross section through the embodiment of FIG. 5 in the region of the fastening pin.
  • FIG. 1 shows a high-pressure pump 10 with a pump housing 12 and a pump unit 13.
  • the high-pressure pump 10 may have further pump units (not shown).
  • the high-pressure pump 10 can be used in particular for high-pressure fuel supply in a storage injection system of an internal combustion engine of a motor vehicle.
  • the pump housing 12 is preferably formed of a metal.
  • the high-pressure pump 10 has centrally a drive shaft 16 which is in operative connection with two cams 20 and is rotatably mounted in the pump housing 12 in a rotation axis D.
  • Compression strokes can be specified via the number of cams 20.
  • the number of conveying or compression strokes corresponds to the number of cams 20.
  • the high pressure pump 10 has two cams 20th
  • the pump unit 13 essentially comprises a cylinder 14 with a cylinder longitudinal axis Z, a cylinder chamber 18 arranged in the cylinder 14, a spring 26, a pump piston 28 and a transfer device 29.
  • the transfer device 29 is mounted in a housing section 12a of the pump housing 12.
  • the transmission device 29 has a longitudinal axis L, which in the embodiment shown here is identical to the cylinder longitudinal axis Z. In the embodiment shown here, the transfer device 29 is designed as a ram assembly.
  • the cylinder 14, the cylinder chamber 18, the spring 26 and the pump piston 28 are arranged coaxially with each other.
  • the cylinder 14 is fixedly coupled to the pump housing 12 and formed of a metal, preferably a steel.
  • the pump piston 28 is mounted axially movable in the cylinder chamber 18 of the cylinder 14 and is connected via the cam 20 with the drive shaft 16 in operative connection.
  • the pump piston 28 is driven in particular by the cams 20 of the drive shaft 16 in a lifting movement in at least approximately radial direction to the axis of rotation D of the drive shaft 16.
  • the pump piston 28 is held in constant contact with the cams 20 of the drive shaft 16 by means of the spring 26, which is preferably designed as a helical compression spring and is preferably supported on the cylinder 14 and on a cylindrical plunger 30.
  • the spring 26 is preferably designed as a helical compression spring and is preferably supported on the cylinder 14 and on a cylindrical plunger 30.
  • the cylinder 14 has an inlet line 22, in which preferably an inlet valve 23 is arranged.
  • the inlet valve 23 he ⁇ facilitates the filling of the cylinder chamber 18 and prevents the Filling the backflow of the fluid from the feed line 22.
  • the cylinder 14 further has a drain line 24 and an outlet valve 25 arranged in this.
  • fluid can be ejected from the cylinder chamber 18.
  • Trained as a ram assembly transmission device 29 includes the cylindrical plunger 30 which is guided within the pump housing 12 in the direction of the cylinder longitudinal axis Z and is in driving connection with the pump piston 28.
  • the pump piston 28 preferably has a smaller diameter than the plunger 30.
  • the pump piston 28 and the plunger 30 may consist of the same or in each case a different material, preferably made of a steel.
  • the plunger 30 is preferably guided on the pump housing 12.
  • the spring 26 is supported on a spring plate 31, which is in engagement with the pump piston 28 and the plunger 30.
  • the plunger 30 has an inner recess 32 in which a roller shoe 34 is at least partially received.
  • a drive shaft 162 facing portion of the roller shoe 34 comprises in the central region a roller recess 36 in which a cylindrical roller 38 is at least partially received and rotatably arranged.
  • the roller recess 36 is adapted to the radial bearing and guidance of the roller 38.
  • the plunger 30 serves for at least indirect support of the pump piston 28 via the rotatably coupled to the plunger 30 Roller 38 on the drive shaft 16.
  • the roller 38 is held by means of a spring 26 via the plunger 30 and the roller shoe 34 on the roller 38 transmitted force into contact with the drive shaft 16, preferably in abutment with the at least one cam 20 of the drive shaft 16, and rolls on the drive shaft 16 and the cam 20 from.
  • the longitudinal axis of the roller 38 is preferably at least approximately parallel to the axis of rotation D of the drive shaft 16.
  • Fig. 2 shows a partial cross section through a first exporting ⁇ approximate shape of the high pressure pump through the pump shaft 50.
  • the roller support 34 may be substantially rotationally symmetrical to the pump axis 50 and the Have the shape of a circular disc.
  • the roller shoe 34 On a side wall 51, the roller shoe 34 has a recess 41.
  • the recess 41 is cylindrical and realized in the form of a blind hole, which is aligned perpendicular to the pump axis 50.
  • a first fastening pin 40 is inserted in the recess 41.
  • Be ⁇ fastening pin 40 may be non-positively or positively secured in the recess 41.
  • the buildin ⁇ actuating pin 40 is supported with a first end in the recess 41 in the form of a press fit.
  • the attachment pin 40 has a pin head 43 at a second end.
  • the pin head 43 is disposed adjacent to the side wall 51.
  • the pin head 43 is arranged in a groove 42 which is formed on an inner side of the plunger 30.
  • the groove 42 is aligned parallel to the pump axis 50 and extends to a bottom 52 of the plunger 30. Thereby, the first fixing pin 40 can be secured in the recess 41 and then the roller shoe 34 are inserted via the bottom in the plunger 30.
  • the plunger 30 has an annularly circumferential on the inside of the plunger 30 web 53. At the web 53 is an upper surface 54 of the roller shoe 34 at.
  • the plunger 30 has on an outer side 55 a second recess 44.
  • the second recess 44 is cylindrical and realized as a blind hole.
  • the second recess 44 is aligned perpendicular to the pump axis 50.
  • a second fastening pin 45 is arranged.
  • the second attachment pin 45 is attached to a first end 46 in the second recess 44. It can thereby be Fixed To ⁇ the second supply pin 45 positively and / or positively fastened in the second recess 44, the first end of the 46th In the illustrated embodiment, the first end 46 of the second attachment pin 45 is attached via a press fit in the second recess 44.
  • the second attachment pin 45 has a second pin head 48 at a second end.
  • the second pin head 48 is arranged in a further groove 47, which is formed on an inner side of the pump housing 12.
  • the further groove 47 is aligned parallel to the pump axis 50.
  • the further groove 47 may be led to an upper end portion of the pump housing 12.
  • the pin heads 43,48 of the first and / or second attachment pin 40, 45 may be circular or elongated in cross-section.
  • Fig. 3 shows a schematic representation of a cross section through the first fixing pin 40 perpendicular to the pump axis 50.
  • the pin head 43 may have a width perpendicular to the longitudinal axis of the groove 42, which is in the region of the width of the first end of the fixing pin 40. From Fig. 2 it can be seen that parallel to the groove 42 of the pin head 43 has a significantly greater width than a pin portion or a first end of the first fastening pin 40.
  • Fig. 4 shows a cross section perpendicular to the pump axis 50 through the second fixing pin 45.
  • the second pin head 48 of the second Fixed To ⁇ supply pin 45 perpendicular to the longitudinal axis of the further groove 47 only a slightly smaller width than a first end 46 of the second Attachment pin 47 have.
  • the pin heads 43,48 its mountings ⁇ supply pins 40,45 are also formed in the form of circular plates.
  • Fig. 5 shows a further embodiment of a high-pressure pump, in which the roller shoe 34, in contrast to the embodiment of Fig. 2 not by means of two fixing pins, but only by means of a single fixing pin 40 rotatably on the pump housing 12 with respect to the Pump axis 50 is guided.
  • the plunger 30 has a hole 56 through which the fastening pin 40 is guided.
  • a first end of the fixing pin 40 is fixed in the recess 41 of the roller shoe 34.
  • the attachment can be executed positively and / or non-positively.
  • the fastening pin is fastened in the recess 41 by means of an interference fit.
  • the fastening pin 40 has at a second end a pin head 43 which is arranged on an outer side 55 of the plunger 30.
  • the pin head 43 is arranged in a further groove of the pump housing 12.
  • the further groove 47 is formed parallel to the pump axis 50 on an inner side of the pump housing ⁇ 12.
  • Fig. 6 shows a cross section perpendicular to the pump axis 50 through the fixing pin 40 of Fig. 5.
  • the pin head 43 is formed in the form of a circular plate.
  • the pin head 43 may also have an elongate shape, which is arranged with its longitudinal axis parallel to the further groove, as explained with reference to FIGS. 3 and 4 for the embodiment of FIG.
  • the roller shoe is e.g. formed as a rotationally symmetrical circular plate with respect to the pump axis 52.
  • the proposed mounting pins a reduction of component tolerances can be achieved.
  • a secure and precise rotation of the roller shoe is possible.
  • complex machining processes can be reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe haute pression comportant : un carter de pompe et un arbre d'entraînement, l'arbre d'entraînement étant monté de manière à pouvoir tourner autour d'un axe de rotation dans le carter de pompe ; un galet, le galet étant monté de manière à pouvoir tourner parallèlement à l'axe de rotation entre l'arbre d'entraînement et un premier côté d'un sabot de galet; un piston de pompe, le piston de pompe étant en appui par une première partie d'extrémité sur un second côté du sabot de galet, le second côté du sabot de galet étant opposé au premier côté du sabot de galet. Le piston de pompe est monté par une seconde extrémité de manière mobile parallèlement à un axe de pompe dans une chambre de cylindre du carter de pompe, un poussoir prend appui sur le second côté du sabot de galet, le poussoir est maintenu de manière mobile sur l'axe de pompe dans une chambre de pompage du carter de pompe, et le sabot de galet est raccordé au carter de pompe de manière solidaire en rotation par rapport à l'axe de pompe et de manière mobile le long de l'axe de pompe par l'intermédiaire d'au moins une tige de fixation.
PCT/EP2016/071898 2015-09-29 2016-09-15 Pompe haute pression WO2017055103A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
KR1020187008884A KR20180048853A (ko) 2015-09-29 2016-09-15 고압 펌프
CN201680057087.3A CN108026903B (zh) 2015-09-29 2016-09-15 高压泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015218754.3A DE102015218754B4 (de) 2015-09-29 2015-09-29 Hochdruckpumpe
DE102015218754.3 2015-09-29

Publications (1)

Publication Number Publication Date
WO2017055103A1 true WO2017055103A1 (fr) 2017-04-06

Family

ID=56926223

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2016/071898 WO2017055103A1 (fr) 2015-09-29 2016-09-15 Pompe haute pression

Country Status (4)

Country Link
KR (1) KR20180048853A (fr)
CN (1) CN108026903B (fr)
DE (1) DE102015218754B4 (fr)
WO (1) WO2017055103A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016224835A1 (de) * 2016-12-13 2018-06-14 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4335685A (en) * 1979-10-19 1982-06-22 Caterpillar Tractor Co. Lifter assembly
DE4227853A1 (de) * 1992-08-22 1994-02-24 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19515191A1 (de) * 1994-04-28 1995-11-02 Nippon Denso Co Hochdruck-Kraftstoffpumpe
DE102010031185A1 (de) 2010-07-09 2012-01-12 Continental Automotive Gmbh Hochdruckpumpe
DE102010026360A1 (de) * 2010-07-07 2012-01-12 Schaeffler Technologies Gmbh & Co. Kg Stössel
DE102010042488A1 (de) * 2010-10-15 2012-04-19 Robert Bosch Gmbh Hochdruckpumpe eines Kraftstoffeinspritzsystems
DE102013100714A1 (de) * 2012-01-31 2013-08-01 Denso Corporation Kraftstoffpumpe
DE102012217801A1 (de) * 2012-09-28 2014-04-03 Schaeffler Technologies Gmbh & Co. Kg Verfahren zur Montage eines Stößel

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004048711B4 (de) * 2004-10-06 2006-09-14 Siemens Ag Radialkolbenpumpe mit Rollenstößel
US7311087B2 (en) 2004-11-23 2007-12-25 Cummins Inc. Fuel pump with a guided tappet assembly and methods for guiding and assembly
DE102009056306A1 (de) 2009-11-30 2011-06-01 Schaeffler Technologies Gmbh & Co. Kg Rollenstößel
EP2853699B1 (fr) 2013-09-27 2016-05-25 Aktiebolaget SKF Poussoir, pompe à injection et actionneur de soupape comportant un tel poussoir et procédé de fabrication d'un tel poussoir

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4335685A (en) * 1979-10-19 1982-06-22 Caterpillar Tractor Co. Lifter assembly
DE4227853A1 (de) * 1992-08-22 1994-02-24 Bosch Gmbh Robert Kraftstoffeinspritzpumpe für Brennkraftmaschinen
DE19515191A1 (de) * 1994-04-28 1995-11-02 Nippon Denso Co Hochdruck-Kraftstoffpumpe
DE102010026360A1 (de) * 2010-07-07 2012-01-12 Schaeffler Technologies Gmbh & Co. Kg Stössel
DE102010031185A1 (de) 2010-07-09 2012-01-12 Continental Automotive Gmbh Hochdruckpumpe
DE102010042488A1 (de) * 2010-10-15 2012-04-19 Robert Bosch Gmbh Hochdruckpumpe eines Kraftstoffeinspritzsystems
DE102013100714A1 (de) * 2012-01-31 2013-08-01 Denso Corporation Kraftstoffpumpe
DE102012217801A1 (de) * 2012-09-28 2014-04-03 Schaeffler Technologies Gmbh & Co. Kg Verfahren zur Montage eines Stößel

Also Published As

Publication number Publication date
DE102015218754B4 (de) 2018-08-30
CN108026903B (zh) 2019-11-05
CN108026903A (zh) 2018-05-11
KR20180048853A (ko) 2018-05-10
DE102015218754A1 (de) 2017-03-30

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