EP1281861A2 - Dispositif d'injection de carburant pour moteurs à combustion interne - Google Patents

Dispositif d'injection de carburant pour moteurs à combustion interne Download PDF

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Publication number
EP1281861A2
EP1281861A2 EP02016714A EP02016714A EP1281861A2 EP 1281861 A2 EP1281861 A2 EP 1281861A2 EP 02016714 A EP02016714 A EP 02016714A EP 02016714 A EP02016714 A EP 02016714A EP 1281861 A2 EP1281861 A2 EP 1281861A2
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection device
piston
guide
housing
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
EP02016714A
Other languages
German (de)
English (en)
Other versions
EP1281861B1 (fr
EP1281861A3 (fr
Inventor
Ngoc-Tam Vu
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.)
LOrange GmbH
Original Assignee
LOrange 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 LOrange GmbH filed Critical LOrange GmbH
Publication of EP1281861A2 publication Critical patent/EP1281861A2/fr
Publication of EP1281861A3 publication Critical patent/EP1281861A3/fr
Application granted granted Critical
Publication of EP1281861B1 publication Critical patent/EP1281861B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
    • 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
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/462—Delivery valves

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1.
  • a high pressure pump worked which is designed as a stamp pump and in Suction stroke via a low pressure source of fuel that is supplied in the compression stroke is fed into a high-pressure accumulator via a valve unit.
  • the valve unit consists of two valve members, one of which acts as a locking piston in the compression cycle Connects to the low pressure source and the other in the suction cycle Connection of the high pressure accumulator to the low pressure source and to the pump work space diverts and is designed as a check piston. Both valve members are in the direction spring-loaded to their respective locking position, the locking piston over the Non-return piston is guided and resiliently supported against the non-return piston, at same direction of action of the spring loading the non-return piston and the Locking piston loading spring.
  • valve unit is in turn guided in an inserted into the pump housing Valve body that clamps axially against the pump housing via a connecting piece is.
  • valves are designed as spherical or poppet valves designed and integrated into the housing of the pressure accumulator arranged, whereby a more cost-effective construction is to be achieved, but with what also the structure of the housing of the partially pulsating high pressure High pressure storage is weakened.
  • the invention has for its object a fuel injection device
  • the aforementioned type is simplified and more manageable in terms of production technology embody.
  • a structure in which the Locking piston and the check piston with regard to the formation of a sealing limit interact with each other, with a transition area between the channel sections running through the check piston and the locking piston in the connection of the pump workspace to the high-pressure accumulator delimited and blocked against the low pressure source.
  • Such a structure is both with respect to the valve members, which are by locking pistons and Non-return pistons are formed, without problems, since these are simple to manufacture have easily manageable shapes and avoid nested guides become.
  • the locking piston and the check piston can be in one continuous housing guide are arranged due to their design can be easily accommodated in the pump housing itself.
  • Furthermore are at Such a solution requires only low spring forces, since in the compression stroke corresponding pressure forces are built up immediately as the pressure builds up. This in turn allows a weakly designed low pressure source, since the suction forces the Valve unit by acting on the locking piston in the sense of an opening against the Affect low pressure source.
  • valve unit can be coaxial to Pump cylinders are provided, the introduction of which is designed as a bore Housing guide for the valve unit in the pump housing also good in terms of production technology is to be mastered.
  • the valve unit can also be in a separate, separate Housing part of the pump housing may be provided, the parting plane preferably with the upper boundary level of the pump work space coincides, so that the Bore for the pump stamp can be designed as a through hole.
  • the Housing guide for the valve unit in the upper end level of the pump housing ends is assigned a covering head part, in which head part the the check piston in the closing direction loading spring can be arranged.
  • the head part also the high-pressure accumulator assign, including the feed holes, or just the feed holes, the first solution in particular leads to a particularly compact unit.
  • the cover of the pump housing with the head part ending at the head part Housing guidance also proves to be particularly useful for the housing guidance in its end tapering towards the head part, an enlarged area assign, the manufacturing technology introduced easily from the free end can be the conical or stepped in the transition to the housing guide System for the non-return piston can form that towards the pump work space subsequently to its diameter interacting with the system enlarged area preferably a diameter compared to the housing guide reduced area to which a guide area of the check piston connects over which it is guided in the housing guide in a sliding and sealing manner.
  • the locking piston via a corresponding one Guide section in the housing guide axially slidably arranged, wherein the locking piston in the area adjacent to the non-return piston preferably in its Outside diameter is reduced to a neck, so that there is a radially outer Shoulder area that acts as the loading area for the low pressure side pressure causes the locking piston to be loaded against its spring force is.
  • the pressurization of the locking piston in the compression cycle leads to a much higher load on the locking piston in the opposite direction, so that supports due to the spring force, a quick reversal and a reliable seal in the Sealing limit between the blocking piston and non-return piston is reached.
  • the fuel injection device 1 each has one in a pump cylinder 40 performed pump ram 3, the one to the pump cylinder 40 volume-variable pump work space 4 delimits.
  • the pump cylinder 40 is from enclosed in a pump jacket 5, pump cylinder 40 and pump jacket 5 together form the pump housing 2, which is covered by a head part 6 upwards are that receives a high pressure accumulator 7 in the exemplary embodiment and that against Pump housing 2, as indicated schematically at 8, is screwed.
  • the pump plunger 3 lies coaxially with one of the pump working space 4 in the same Extension in the direction of the head part 6 lying hole 9, which has a Transition bore 10 of smaller diameter to the pump work space 4 is connected and which in the covered by the head part 6 end face 11 of the Pump housing 2 runs out.
  • the bore 9 forms a housing guide 12 for one Valve unit 13, which comprises two valve members, one of which is a non-return piston 14 and the other forms a locking piston 15.
  • Check piston 14 and locking piston 15 are coaxial and lying one behind the other in the axial direction in the bore 9 added, the locking piston 15 adjacent to the pump work chamber 4 and the Check piston 14 is adjacent to the pressure accumulator 7 and each other facing end faces of check pistons 14 and locking pistons 15, which have springs 16 and 17 are loaded against each other, determine a sealing limit 18.
  • This Sealing limit 18 lies axially in the region of a radially widening the housing guide 12 Ring zone 19, the holes 20 and an annular space 21 in the transition between the Pump cylinder 40 and the jacket 5 with a low pressure source, not shown is connected, the connection passing through the jacket 5 being dashed at 22 is indicated.
  • the check piston 14 and the locking piston 15 each have a center Axial bore 23 or 24, wherein the axial bores in from the sealing limit 18th enclosed area the channel sections of this transition area between Check piston 14 and locking piston 15 form and wherein the axial bore 24 of the Locking piston 15 penetrates this over the entire length and in the direction of the Pump working space 4 extends to a spring cup 25, in which the spring 17 engages, which are opposite to the locking piston 15 in the transition of the bore 9 to the Bore 10 is supported against the pump cylinder 40.
  • the locking piston 15 In the area of its end associated with the sealing limit 18, the locking piston 15 is in the Radially included from the outside, so that it runs out against the sealing limit 18 tapered neck 26 is formed, which forms the front end of the sealing zone, which, based on the 1 and 2, as part of a flat seal forming the sealing boundary 18 against the opposite end of the check piston 14 in the compression stroke is present and thereby the connection from the pump work space 4 to the pressure accumulator 7 delimited against the low pressure source.
  • the axial bore 23 in the check piston 14 runs over one or more transverse bores 27 on an annular space 28, the axially between the guide part 29 of the check piston 14, which is adjacent to the sealing limit 18 and whose region 30 is enlarged in diameter and axially overlaps one in diameter enlarged area 31 of the bore 9 is located in the Housing guide 12 forming part of the bore 9 in a system 32 against which the check piston 14 in the suction stroke pressure and spring loaded with a corresponding Stop surface of the area 30 with a larger diameter lies sealingly.
  • the spring 16 loading the non-return piston 14 is of a spring cup 33 as Bore extension of the bore 34 running out on the pressure accumulator 7 recorded and supported axially opposite to the check piston 4 against the Headboard 6 from.
  • Fig. 1 illustrates the suction cycle with the passage of the low pressure source
  • Fuel fed into the pump work space 4 in the enlarged section 2 is a corresponding representation for the compression stroke, in which the pump work space 4 is connected to the pressure accumulator 7, at the Density limit 18 formed shut-off against the low pressure source, in which Compression stroke via the pressurization of the locking piston 15
  • Check piston 14 is raised in the direction of the head part 6, so that the flow released from the annular space 28 to the area 31 and from there to the pressure accumulator 7 is.
  • valve unit 13 is reversed in the suction cycle by pressure and spring loading with respect to the check piston 14 so that it assumes a blocking position, at simultaneous action on the low-pressure side of the locking piston 15 against the Supporting force of the spring 17 is by the suction pressure in the pump work chamber 4.
  • sealing limit 35 which, in contrast to the illustration 1 is not designed with a flat seat, but with a conical seat.
  • the check piston 14 of otherwise identical design now on its locking piston 15 facing end face with a conical or concave recess 36 provided that on the part of the locking piston 15 corresponds to a neck 26 having a conical or has convexly curved outlet 37, which forms the compression stroke Sealing limit 35 engages in the recess 36.
  • valve unit 13 of the fuel injection device according to the invention is distinguished by great simplicity, depending on the respective pump cycle - suction cycle or compression cycle - the connection of the pump work space 4 to the Low pressure side or to the high pressure accumulator is controlled via the locking piston 15.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP02016714A 2001-07-30 2002-07-26 Dispositif d'injection de carburant pour moteurs à combustion interne Expired - Lifetime EP1281861B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10136926 2001-07-30
DE10136926A DE10136926C1 (de) 2001-07-30 2001-07-30 Kraftstoff-Einspritzeinrichtung für Brennkraftmaschinen

Publications (3)

Publication Number Publication Date
EP1281861A2 true EP1281861A2 (fr) 2003-02-05
EP1281861A3 EP1281861A3 (fr) 2003-04-23
EP1281861B1 EP1281861B1 (fr) 2004-05-19

Family

ID=7693480

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02016714A Expired - Lifetime EP1281861B1 (fr) 2001-07-30 2002-07-26 Dispositif d'injection de carburant pour moteurs à combustion interne

Country Status (3)

Country Link
EP (1) EP1281861B1 (fr)
AT (1) ATE267340T1 (fr)
DE (2) DE10136926C1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT504433B1 (de) * 2006-11-07 2008-05-15 Bosch Gmbh Robert Pumpenelement für eine common-rail-hochdruckpumpe
WO2011003789A1 (fr) * 2009-07-08 2011-01-13 Delphi Technologies Holding S.À.R.L. Unité pompe
ITTO20090715A1 (it) * 2009-09-21 2011-03-22 Torino Politecnico Gruppo pompa perfezionato per un apparato di iniezione di un motore a combustione interna
EP2522854A1 (fr) * 2011-05-09 2012-11-14 Robert Bosch Gmbh Agencement de soupape pour une pompe à carburant haute pression ainsi qu'une pompe à carburant haute pression

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5064354A (en) * 1990-06-04 1991-11-12 Robertson Walter W High pressure fluid pump
US5605449A (en) * 1996-01-25 1997-02-25 Wendy Buskop Suction and discharge valve arrangement for a high pressure piston pump
WO1997017538A1 (fr) * 1995-11-08 1997-05-15 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0990792A3 (fr) * 1998-09-30 2003-05-21 CRT Common Rail Technologies AG Système d'injection de carburant de type Common-Rail

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5064354A (en) * 1990-06-04 1991-11-12 Robertson Walter W High pressure fluid pump
WO1997017538A1 (fr) * 1995-11-08 1997-05-15 Robert Bosch Gmbh Dispositif d'injection de carburant pour moteurs a combustion interne
US5605449A (en) * 1996-01-25 1997-02-25 Wendy Buskop Suction and discharge valve arrangement for a high pressure piston pump

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT504433B1 (de) * 2006-11-07 2008-05-15 Bosch Gmbh Robert Pumpenelement für eine common-rail-hochdruckpumpe
WO2011003789A1 (fr) * 2009-07-08 2011-01-13 Delphi Technologies Holding S.À.R.L. Unité pompe
EP2287462A1 (fr) * 2009-07-08 2011-02-23 Delphi Technologies Holding S.à.r.l. Unité de pompe
CN102472220A (zh) * 2009-07-08 2012-05-23 德尔福技术控股有限公司 泵单元
JP2012533010A (ja) * 2009-07-08 2012-12-20 デルファイ・テクノロジーズ・ホールディング・エス．アー．エール．エル． ポンプ装置
CN102472220B (zh) * 2009-07-08 2014-05-14 德尔福技术控股有限公司 泵单元
US10041457B2 (en) 2009-07-08 2018-08-07 Delphi Technologies Ip Limited Pump unit
ITTO20090715A1 (it) * 2009-09-21 2011-03-22 Torino Politecnico Gruppo pompa perfezionato per un apparato di iniezione di un motore a combustione interna
EP2522854A1 (fr) * 2011-05-09 2012-11-14 Robert Bosch Gmbh Agencement de soupape pour une pompe à carburant haute pression ainsi qu'une pompe à carburant haute pression

Also Published As

Publication number Publication date
EP1281861B1 (fr) 2004-05-19
DE10136926C1 (de) 2003-01-16
ATE267340T1 (de) 2004-06-15
DE50200457D1 (de) 2004-06-24
EP1281861A3 (fr) 2003-04-23

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