EP3094855A1 - Dispositif de poussoir à galet et procédé de production de dispositif de poussoir à galet - Google Patents

Dispositif de poussoir à galet et procédé de production de dispositif de poussoir à galet

Info

Publication number
EP3094855A1
EP3094855A1 EP15721682.1A EP15721682A EP3094855A1 EP 3094855 A1 EP3094855 A1 EP 3094855A1 EP 15721682 A EP15721682 A EP 15721682A EP 3094855 A1 EP3094855 A1 EP 3094855A1
Authority
EP
European Patent Office
Prior art keywords
bearing shell
housing
roller
plunger
circumferential surface
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
EP15721682.1A
Other languages
German (de)
English (en)
Other versions
EP3094855B1 (fr
Inventor
Stefan Roider
Ludwig Kirschenhofer
Detlef Haupt
Christian Kemna
Martin Schmidt
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.)
Continental Automotive GmbH
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
Publication of EP3094855A1 publication Critical patent/EP3094855A1/fr
Application granted granted Critical
Publication of EP3094855B1 publication Critical patent/EP3094855B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F04B1/0413—Cams
    • F04B1/0417—Cams consisting of two or more cylindrical elements, e.g. rollers
    • 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
    • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
    • F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
    • F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
    • F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams

Definitions

  • the present invention relates to a roller tappet device for a pump and to a corresponding method for producing the roller tappet device.
  • the object of the invention is to provide a roller tappet device for a pump, which contributes to a reliable and efficient operation of the pump. It is another object of the invention to provide a corresponding method for producing the roller tappet device.
  • the invention is characterized by a roller tappet device for a pump, comprising a plunger with a longitudinal axis, a plunger housing with a In ⁇ nenmantel structure, a bearing shell with an outer circumferential surface, and a roller with a rotation axis.
  • the bearing shell has a bearing shell recess in which the roller is rotatably mounted. Furthermore, the bearing shell on a side facing away from the LagerschalenausEnglishung a pin which is received in a housing bearing of the plunger housing.
  • the bearing shell is fixedly coupled to the plunger housing via an outer circumferential surface of the journal and an inner circumferential surface of the housing bearing.
  • the roller is supported on a drive device of the pump. The roller is also designed to transmit a force from the drive device via the bearing shell to the plunger along the longitudinal axis during operation of the pump.
  • the pump is a high-pressure fuel pump, for example, a high-pressure diesel pump.
  • the drive device comprises, in particular, a cam on which the roller is supported, for example.
  • the roller tappet device is designed to put a rotational movement of the cam switch ⁇ into a linear movement along the longitudinal axis.
  • a diameter of the pin is less than 75% of a diameter of the inner surface of the Tappet housing. In a further embodiment, the diameter of the pin is in particular less than 35% of the diameter of the inner circumferential surface of the plunger housing.
  • the bearing shell and the plunger housing for example, have corresponding openings, which allow fluid flow along the longitudinal axis.
  • the outer circumferential surface of the pin and the inner circumferential surface of the housing bearing are fixedly coupled by means of a press fit.
  • the interference fit allows a reliable, cost-effective coupling of the bearing shell with the plunger housing.
  • the interference fit is an oil press dressing.
  • the bearing shell recess facing away from the bearing shell on a bearing shell stop surface.
  • the bearing shell facing side of the plunger housing has a housing stop surface. The bearing shell stop surface and the housing stop surface are formed parallel to each other.
  • the mutually parallel stop surfaces is contributed to a perpendicularity of a rotation axis of the roller and the longitudinal axis.
  • this enables an efficient and reliable operation of the roller tappet device.
  • the parallel stop ⁇ surfaces are parallel to the axis of rotation of the roller.
  • the inner lateral surface of the tappet housing is designed to limit an offset of the roller in the direction of the axis of rotation. Limiting the offset of the roller in the direction of the axis of rotation contributes to an efficient and reliable operation of the roller tappet device.
  • the inner circumferential surface of the plunger housing has two flat, mutually diametrical contact surfaces, which are designed to limit the displacement of the roller in the direction of the axis of rotation.
  • the roll is thus particularly efficiently contributed to limiting the offset.
  • the contact surfaces are in particular parallel to the longitudinal axis.
  • At least one bearing shell part region of the outer circumferential surface of the bearing shell and a respective housing ⁇ partial region of the inner circumferential surface of the plunger housing are formed parallel to each other curved such that a torque with respect to the longitudinal axis of the bearing shell on the
  • Plunger housing is transferable.
  • this helps to prevent a rotation of the bearing shell with respect to the plunger housing.
  • a VerFDbegrenzung the bearing shell contributes, for example, during assembly of the roller tappet ⁇ device that the fixed coupling of the bearing shell can be done with the plunger housing.
  • functional decoupling of the Verfbegrenzung means of the outer circumferential surface of the bearing shell of the fixed coupling of the bearing shell by means of the outer surface of the pin, for example, a variable geometry of the inner circumferential surface of the plunger housing is made possible, so that a particularly advantageous limitation of the offset of the role in the direction of the axis of rotation is contributed.
  • the outer circumferential surface of the bearing shell for limiting the rotation is rotationally asymmetrical with respect to the longitudinal axis.
  • the at least one bearing shell part region and the respective housing part region are planar.
  • the outer circumferential surface of the bearing shell at least two diametrically parallel planar bearing shell portions, as well as the inner circumferential surface of the plunger housing corresponding thereto in each case at least two diametrically parallel flat housing partial areas.
  • the at least one bearing shell portion and the at least one housing portion may also be referred to as key surfaces.
  • the invention is characterized by a method for producing a roller tappet device for a pump according to the first aspect, wherein a plunger with a longitudinal axis, a plunger housing with an inner circumferential surface, a bearing shell with an outer circumferential surface, and a roller with a rotation axis to be provided.
  • the bearing shell has a bearing shell recess in which the roller is rotatably mounted. Furthermore, the bearing shell on a side facing away from the LagerschalenausEnglishung a pin which is received in a housing bearing of the plunger housing.
  • the bearing shell is fixedly connected to the plunger housing via a predominantlyman ⁇ telology of the pin and an inner circumferential surface of the housing ⁇ bearing fixed by means of interference fit.
  • the roller is supported on a drive device of the pump.
  • the roller tappet device has a VerFDbe ⁇ limitation of the bearing shell with respect to the plunger housing, for example by at least one bearing shell portion of the outer circumferential surface of the bearing shell and a respective housing ⁇ partial region of the inner circumferential surface of the plunger housing are formed parallel to each other curved such that a torque with respect to the longitudinal axis of the bearing shell is transferable to the plunger ⁇ housing, it is helped that a pressing of the bearing shell can be done with the plunger housing.
  • the bearing shell by means of the VerFDbegrenzung with respect to the plunger housing initially from ⁇ directed and then pressed.
  • Figure 2 is a perspective view of a bearing shell of the roller tappet device according to Figure 1
  • Figure 3 is a perspective view of a plunger housing of the roller tappet device according to Figure 1
  • Figure 4 is a perspective view of
  • a roller tappet device 1 for a pump in particular for a high-pressure fuel pump, comprises a tappet 3 with a longitudinal axis L (FIG. 1).
  • the roller tappet device 1 further comprises a plunger housing 5, a bearing shell 7, and a roller 9, for example, the axisymmetric with respect to the
  • the pump for example, a diesel ⁇ high pressure pump.
  • the pump is, for example, a gasoline high pressure pump.
  • the pump has, for example, a drive device, a pump housing, and a piston (not shown in detail).
  • the piston of the pump is coupled, for example, with the plunger 3.
  • the drive device comprises, for example, a shaft with a cam on which the roller is supported.
  • a rotational movement of the cam is converted into a linear movement of the roller tappet device 1 along the longitudinal axis L.
  • the roller 9 is rotatably mounted in this context about an axis of rotation D, so that is contributed to a rei ⁇ low-friction rolling of the cam.
  • the plunger housing 5 is guided with its Au ⁇ zmantel components 10 in the pump housing, so that in operation of the pump to a precise linear movement of
  • Roller plunger device along the longitudinal axis L is contributed.
  • a force transmission of the cam takes place during operation of the pump via the roller tappet device 1 on the piston.
  • the bearing shell 7 has a pin 11 with an outer circumferential surface 12. On the pin 11 sits, for example, the 0
  • the bearing shell 7 also has, for example, at least one bearing shell opening 13, which allows fluid flow along the longitudinal axis L (FIG. 2). Furthermore, the bearing shell 7 has two opposite bearing shell subareas 15 on its outer lateral surface 16, a bearing shell abutment surface 17, and facing away from this a bearing shell recess 19, which is designed to receive the roller 9.
  • the tappet housing 5 is formed, the bearing shell réelle take ⁇ . 7
  • the plunger housing 5 a housing bearing 21 with an inner circumferential surface 22 ( Figure 3), in which the pin 11 is inserted.
  • the plunger housing 5, for example, further comprises at least one housing opening 23, which corresponds in particular to the respective bearing shell opening 13.
  • the plunger housing 5 has two opposite housing partial regions 25 on its inner lateral surface 26, which correspond to the bearing shell partial regions 15 of the bearing shell 7. Furthermore, the plunger housing 5 has a housing ⁇ stop surface 27, which corresponds to the bearing shell stop surface 17 of the bearing shell 7.
  • the outer circumferential surface 16 of the bearing shell 7 and the inner lateral surface 26 of the tappet housing 5 are in particular rotationally asymmetrical with respect to the longitudinal axis L.
  • rotation of the bearing shell 7 is limited in the plunger housing 5 about the longitudinal axis L. Furthermore, this allows alignment of the bearing shell 7 with respect to the plunger housing 5 during assembly of the roller tappet device first
  • the bearing shell portions 15 and the housing portions 25 are flat and parallel to each other.
  • the bearing shell portions 15 and the housing ⁇ partial areas 25 may also be referred to as a key surface-like geometry.
  • the housing stop surface 27 limits an offset of the La ⁇ gerschale 7 along the longitudinal axis L with respect to the plunger housing 5 in the direction of the plunger 3.
  • the housing stop surface 27 is for example on the bearing shell stop surface 17.
  • the bearing shell stop surface 17 and the GeHouseanschlag- surface 27 are formed parallel to each other in this context, in particular parallel to the axis of rotation D of the roller 9.
  • a precise alignment of the bearing shell 7 with the roller 9 with respect to the longitudinal axis L he ⁇ allows.
  • a perpendicularity of the axis of rotation D with respect to the longitudinal axis L is contributed.
  • the outer circumferential surface 12 of the pin 11 is fixedly coupled to the inner lateral surface 22 of the housing bearing 21.
  • the bearing shell 7 is fixed in particular via a press fit on the outer circumferential surface 12 of the pin 11 with the plunger housing 5 on the inner circumferential surface 22 of the housing bearing 21, wherein a diameter of the press dressing is less than 75% of a diameter of the outer circumferential surface 16 of the bearing shell 7.
  • the diameter of the press fit is less than 35% of the diameter of the outer circumferential surface 16 of the bearing shell 7.
  • surfaces of the bearing shell 7 bezie ⁇ tion of the plunger housing 5 to align the bearing shell 7 with respect to the plunger housing 5 functionally separated from surfaces for fixing the bearing shell 7 with respect to the plunger housing 5.
  • This allows a variable design of the inner circumferential surface 26 of the plunger housing 5, in particular With regard to the bearing of the roller 9.
  • a force acts on the roller 9 in the direction of the rotation axis D.
  • the inner circumferential surface 26 of the plunger housing 5 is formed in this context to limit an offset of the roller 9 in the direction of the rotation axis D.
  • the inner lateral surface 26 of the tappet housing 5 has contact surfaces 29 opposite thereto (see also FIG. 1).
  • the contact surfaces 29 may be formed, for example, each as a flat contact surface with respect to the roller 9.
  • Figure 4 shows a perspective view of the roller tappet ⁇ device 1 according to figure 1 along the longitudinal axis L.
  • a roller tappet ⁇ device 1 allows a decoupling of the press fit of the outer surface 10 of the tappet housing 5 for guidance in the pump casing.
  • decoupling of the press fit from a bearing surface 30 (see FIG. 2) of the bearing shell recess 19 allows for radial roller guide.
  • such a roller tappet device 1 contributes to an immediate power line between the piston and the bearing shell 7.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne un dispositif de poussoir à galet (1), destiné à une pompe, qui comprend un poussoir (3) pourvu d'un axe longitudinal (L), un boîtier de poussoir (5) pourvu d'une surface d'enveloppe intérieure (26), une coquille de palier (7) pourvue d'une surface d'enveloppe extérieure (16) et un galet (9) pourvu d'un axe de rotation (D) ; la coquille de palier (7) comporte une cavité (19) dans laquelle le galet (9) est monté à rotation et la coquille de palier (7) comporte, sur un côté opposé à la cavité (19), un pivot (11) qui est logé dans un palier (21) du boîtier de poussoir (5) ; la coquille de palier (7) est accouplé solidairement par le biais d'une surface d'enveloppe extérieure (12) du pivot (11) et d'une surface d'enveloppe intérieure (22) du palier (21) au boîtier de vérin (5) et le galet (9) est supporté par un dispositif d'entraînement de la pompe et est configuré pour transmettre, pendant le fonctionnement de la pompe, une force du dispositif d'entraînement au poussoir (3), par le biais de la coquille de palier (7), le long de l'axe longitudinal (l).
EP15721682.1A 2014-10-15 2015-05-06 Dispositif de poussoir à galet et procédé de production de dispositif de poussoir à galet Not-in-force EP3094855B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014220881.5A DE102014220881A1 (de) 2014-10-15 2014-10-15 Rollenstößelvorrichtung und Verfahren zur Herstellung einer Rollenstößelvorrichtung
PCT/EP2015/059891 WO2016058712A1 (fr) 2014-10-15 2015-05-06 Dispositif de poussoir à galet et procédé de production de dispositif de poussoir à galet

Publications (2)

Publication Number Publication Date
EP3094855A1 true EP3094855A1 (fr) 2016-11-23
EP3094855B1 EP3094855B1 (fr) 2018-07-11

Family

ID=53175034

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15721682.1A Not-in-force EP3094855B1 (fr) 2014-10-15 2015-05-06 Dispositif de poussoir à galet et procédé de production de dispositif de poussoir à galet

Country Status (6)

Country Link
US (1) US20170204824A1 (fr)
EP (1) EP3094855B1 (fr)
KR (1) KR101908832B1 (fr)
CN (1) CN106103986B (fr)
DE (1) DE102014220881A1 (fr)
WO (1) WO2016058712A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019102289B3 (de) * 2019-01-30 2020-03-05 Schaeffler Technologies AG & Co. KG Rollenstößel für eine Kraftstoffpumpe
DE102019118891A1 (de) * 2019-07-12 2021-01-14 Schaeffler Technologies AG & Co. KG Rollenstößel für eine Kraftstoffhochdruckpumpe

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1776119A1 (de) * 1968-09-24 1971-10-07 Orange Gmbh Einspritzpumpe
US3822683A (en) * 1972-12-11 1974-07-09 Caterpillar Tractor Co Roller bearing retaining clip
US5566652A (en) * 1995-10-06 1996-10-22 Eaton Corporation Light weight cam follower
SI9600292A (sl) * 1996-10-02 1998-04-30 Mag. Manfreda Jurij, Dipl.Ing. Batni sklop radialno-batnega hidravličnega stroja
EP1557558B1 (fr) * 2002-10-29 2018-01-31 Bosch Automotive Systems Corporation Pompe d'alimentation en carburant et corps à structure poussoir
CN1714236A (zh) * 2003-01-09 2005-12-28 株式会社博世汽车系统 燃料供给用泵
US20050100466A1 (en) * 2003-01-09 2005-05-12 Nobuo Aoki Fuel supply pump
JP2004324537A (ja) * 2003-04-24 2004-11-18 Bosch Automotive Systems Corp 燃料供給用ポンプおよびタペット構造体
DE10355027A1 (de) * 2003-11-25 2005-06-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
WO2005068823A1 (fr) * 2004-01-14 2005-07-28 Bosch Corporation Pompe d'alimentation en carburant
DE102006028348B3 (de) * 2006-06-20 2007-10-31 Siemens Ag Rollenlagerungsvorrichtung
CN102027235A (zh) * 2008-05-12 2011-04-20 Ntn株式会社 泵用挺杆
JP4930478B2 (ja) * 2008-09-04 2012-05-16 トヨタ自動車株式会社 ローラリフタ、ローラリフタの製造方法、および液体用ポンプ
DE102009028392B4 (de) * 2009-08-10 2018-05-24 Robert Bosch Gmbh Hochdruckpumpe

Also Published As

Publication number Publication date
CN106103986A (zh) 2016-11-09
US20170204824A1 (en) 2017-07-20
EP3094855B1 (fr) 2018-07-11
KR20160132985A (ko) 2016-11-21
DE102014220881A1 (de) 2016-04-21
WO2016058712A1 (fr) 2016-04-21
CN106103986B (zh) 2017-11-28
KR101908832B1 (ko) 2018-10-16

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