EP0910738B1 - Kraftstoffeinspritzpumpe der verteilerbauart - Google Patents

Kraftstoffeinspritzpumpe der verteilerbauart Download PDF

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Publication number
EP0910738B1
EP0910738B1 EP98912281A EP98912281A EP0910738B1 EP 0910738 B1 EP0910738 B1 EP 0910738B1 EP 98912281 A EP98912281 A EP 98912281A EP 98912281 A EP98912281 A EP 98912281A EP 0910738 B1 EP0910738 B1 EP 0910738B1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
space
injection pump
pump according
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.)
Expired - Lifetime
Application number
EP98912281A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0910738A1 (de
Inventor
Heinz Nothdurft
Nestor Rodriguez-Amaya
Andreas Dutt
Hubert Greif
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 EP0910738A1 publication Critical patent/EP0910738A1/de
Application granted granted Critical
Publication of EP0910738B1 publication Critical patent/EP0910738B1/de
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
    • 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
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • 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
    • F02M41/00—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor
    • F02M41/08—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined
    • F02M41/14—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons
    • F02M41/1405—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis
    • F02M41/1411—Fuel-injection apparatus with two or more injectors fed from a common pressure-source sequentially by means of a distributor the distributor and pumping elements being combined rotary distributor supporting pump pistons pistons being disposed radially with respect to rotation axis characterised by means for varying fuel delivery or injection timing

Definitions

  • the invention relates to a fuel injection pump Distribution type according to the preamble of claim 1 out.
  • Fuel injection pumps are several across the direction of rotation the pump piston located in the distributor, in Art a radial piston pump with enclosed in between Pump chamber.
  • the fuel supply for the Pump work space and its relief serving Connection line has in this known Fuel injection pump a constant, unthrottled Cross-section. With these pumps, the whole Suction stroke of the pump piston fuel when the valve is open sucked in and to determine the effective stroke of the Pump piston then closed the valve again. For one then promotes certain range of rotation angle or time period Fuel injection pump fuel that is on high Injecting pressure is brought to one Fuel injection valve, depending on the position of the distributor.
  • the valve is opened again.
  • the pressure in the pump workspace is the same as before was at a very high level, for example 1000 - 1200 bar, degraded through the valve opening to the low pressure area, by outflowing fuel there and also the the remaining quantity delivered by the pump piston is pushed out.
  • the fuel injection pump according to the invention with the Features of the characterizing part of claim 1 has the compared to the advantage that the narrowing of the diameter in the connecting line which has a cavitation erosion triggering effects are prevented. Due to the The narrowing of the diameter of the fuel takes place in the certain dimensions throttled or at least such that the fuel flowing out through the valve opening quickly certain counter pressure is opposed so that the outflowing fuel from the valve seat is not so can relax that there is an unfavorable flow and too Gas bubbles form in the fuel. Before one continuous flow in the outflow direction over the Has set up the connecting line, the Diameter narrowing currently has a high throttling effect available to build up pressure quickly in the second Valve chamber leads.
  • the connecting line with its axis in the direction of the valve member aligned so that in this way flow of fuel exchange between Low pressure area and pump work space or vice versa can be done.
  • Claim 3 designed the diameter constriction so that a flow of fuel from the low pressure area to Valve opening or to the pump workspace favored.
  • the funnel-shaped design ensures that the Pump work room during the suction phase of the Distributor injection pump sufficiently and quickly with Fuel is supplied without the Diameter narrowing here harmful to the degree of filling of the Pump work room affects.
  • Design as a diffuser Flow conditions continue to improve. Such measures are in the opposite direction, i.e. for fuel leakage not from the pump work room to the low pressure area provided in particular for the initial throttling if the flow through the Connection line to reduce gas bubble formation receive.
  • Connecting lines provided according to claim 7, so that the instantaneous back pressure described above immediately after reopening the valve member to end the high pressure injection evenly can build up so that the formation of insular Gas bubble fields is avoided. It is advantageous if one of the connecting lines is opposite that of the first Valve chamber discharging pressure channel is arranged horizontally, so that from the first pressure channel through the valve opening in the amount of fuel flowing directly into the second valve chamber on the throttled outlet of one of the connecting lines meets. It is in all cases according to claim 13 important for the formation of the counter pressure if on A closing piston is arranged in the valve closing member with the valve closing member via a connecting pin and which is connected to the 2nd valve chamber forms an annulus. The thus according to claim 12 enclosed space promotes the formation of counter pressure and serves thus to reduce the tendency to cavitation.
  • FIG. 1 shows a section through a Distributor injection pump according to standard technology
  • Figure 2 the essential part of the electrically controlled Switching valve with the arrangement of the invention Formation of the connecting line
  • Figure 3 shows a section by the embodiment of Figure 2 along the Line III-III.
  • Fuel injection pump shown in sections of the Distribution type knows one not to be seen here Pump housing on that from a pump head 10th is liquid-tight. Between the pump housing and pump head is therefore a not described Low pressure area 45 included, the same time Low pressure supply area is.
  • a cylinder sleeve 14 used with its inner bore 22 serves to mount a distributor shaft 11. This will from a drive shaft, not shown, via a Driver 12 driven in rotation and is in the axial direction stored fixed.
  • projecting collar 9 is at least one transverse bore 25 introduced, are stored in the pump piston 17, the enclose a pump work space 18 between them.
  • the Pump pistons are surrounded by a circumference surrounding cam ring, not shown here Carrying out a conveying stroke towards the inside Pump room 18 driven and driven on a Outward cam flank a suction stroke carry out.
  • the pump work space 18 is above a Delivery line 19 in constant communication with a Distributor opening 20 in the outer surface of the distributor shaft and is usually from the surface of the Inner bore 22 of the Zynder sleeve 14 covered.
  • this distributor opening lead with angular displacement Injection lines 21 from the inner bore 22 of the From the cylinder sleeve, which may have a pressure valve 13th with fuel injection valves not shown here are connected.
  • a pressure channel continues from the distributor opening 20 46 to a first valve chamber 36, which is part of a Valve member 35 surrounds.
  • This has a guide part 37 which is guided in a guide bore part 38, wherein this guide bore part 38 is part of a recess, the coaxial from the front side 39 of the distributor shaft in this is introduced.
  • the valve member 35 is in the Guide member 37 axially movable and closes with the Guide part 37 which is located on the guide bore part 38 subsequent first valve chamber 36 to the outside. Is to to say that the part of the Distributor shaft protruding from the cylinder sleeve Low pressure area adjacent.
  • an electromagnetic actuator 16 with an armature 54, a solenoid coil 49, which excites this armature pulls a magnetic core and one with the armature 54 connected plunger 51, which is coaxial to the valve member 35 acts.
  • the housing of the electromagnetic actuator 16 closes together with the distributor shaft and cylinder sleeve 14 a space in the pump head 10, which via a channel 8 in permanent connection with the low pressure area 45.
  • the valve member 35 has a valve sealing surface 32 which a valve seat 34 under the influence of the magnetic force of the electromagnetic actuator 16 to the system comes.
  • the valve member closes one of the valve seats 34 surrounded valve opening 32, which connects between the first valve space 36 and a second valve space 24 forms.
  • the spring chamber is no further in pressure relieved as shown.
  • the compensation piston 43 is via a connecting pin 56 with the valve member 35 integrally connected such that the second valve chamber designed as an annulus.
  • the second valve chamber 24 is always closed Low pressure area 45 relieved.
  • Valve member 35 When the distributor injection pump is operated, this becomes Valve member 35 during this suction stroke of the pump piston 17 opened so that the connection described above Fuel from the low pressure area 45 over the first Valve chamber 36, the pressure channel 46, the distributor opening 20 and the delivery line 19 into the pump work space 18 can reach. From a certain point in time Inward movement of the pump piston 17, the desired one Start of injection, the valve member 35 by the electromagnetic actuator 16 closed. The now enclosed in the pump work space 18 Fuel volume is brought to high pressure and in the Follow via the pressure line 19 and the distributor opening 20 promoted to one of the injection lines 21. To finish the injection or to determine the injection quantity the valve member 35 is brought back into the open state, what by interrupting the power supply of the electromagnetic actuator 16 takes place. From this Point, the pressure in the pump work space 18 can second valve chamber 24 and from there to the low pressure region 45 dismantle.
  • FIG. 1 The Connection line 27 of Figure 1 is now as Called connecting line 127. This runs in the Drawing diagonally upwards in the direction of valve opening 33 and forms with the valve seat side wall of the second Valve chamber 24 an angle ⁇ , which is greater than 90 °. in the preferred embodiment shown here this angle is about 135 °.
  • the junction of the connecting line 127 in the second valve space is about half of it Longitudinal extension between valve seat 34 or Valve sealing surface 32 and the compensating piston 43. Die Peculiarity with this as a channel Connection line is that it is from a initially larger diameter to the second valve chamber 24 down into a diameter constriction 57, which with constant diameter directly in the second Valve chamber 24 opens out. Between constriction 57 and the larger diameter part 58 of the Connecting line 127, a transition 60 is provided, the in the example shown funnel-shaped to the second valve chamber 24 is designed to be indicative.
  • the edgy one here Execution can also be provided with rounded transitions his. It can also be this transition 60 and the Diameter narrowing 57 are formed like a diffuser, So with streamlined continuous transitions seen larger diameter in the outflow direction. In all Such a diffuser provides flow directions fluid introduction of liquid available.
  • the connecting line 127 is in constant communication with an annular groove 129, which corresponds to the annular groove 29 of Figure 1 and now into the outer surface of the cylinder sleeve 14 is introduced and also in constant contact with the low pressure region 45.
  • spring chamber 23 now shown Connection 22 to one leading out of the pump is not shown channel.
  • connection line 127 not only one Connection line 127 but the three are provided namely at an even angular distance.
  • the confluence the diameter constrictions 57 lie in one common radial plane to the axis of the distributor shaft.
  • a of these connecting lines 127 as can be seen here, in a radial plane of the mouth of the pressure channel across from.
  • these junctions are axially offset to each other, since they open into different valve rooms.
  • the cross sections of the constrictions are like this dimensioned that in the filling mode of the pump workspace sufficient inflow cross section is available and the Pump work space must also be filled with sufficient suction stroke can.
  • the high proportion of wall that now consists of several holes existing inflow favors the initial rapid Pressure build-up in the event of relief of the pump work space.
EP98912281A 1997-04-25 1998-02-20 Kraftstoffeinspritzpumpe der verteilerbauart Expired - Lifetime EP0910738B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19717494A DE19717494A1 (de) 1997-04-25 1997-04-25 Kraftstoffeinspritzpumpe der Verteilerbauart
DE19717494 1997-04-25
PCT/DE1998/000507 WO1998049441A1 (de) 1997-04-25 1998-02-20 Kraftstoffeinspritzpumpe der verteilerbauart

Publications (2)

Publication Number Publication Date
EP0910738A1 EP0910738A1 (de) 1999-04-28
EP0910738B1 true EP0910738B1 (de) 2002-05-15

Family

ID=7827734

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98912281A Expired - Lifetime EP0910738B1 (de) 1997-04-25 1998-02-20 Kraftstoffeinspritzpumpe der verteilerbauart

Country Status (6)

Country Link
US (1) US6280160B1 (ja)
EP (1) EP0910738B1 (ja)
JP (1) JP2000513784A (ja)
CN (1) CN1083935C (ja)
DE (2) DE19717494A1 (ja)
WO (1) WO1998049441A1 (ja)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10040522A1 (de) * 2000-08-18 2002-02-28 Bosch Gmbh Robert Kraftstoffeinspritzsystem für Brennkraftmaschinen
DE10058011A1 (de) * 2000-11-23 2002-05-29 Bosch Gmbh Robert Magnetventilgesteuerte Kraftstoffeinspritzpumpe für Brennkraftmaschinen, insbesondere Dieselmotoren
DE10059424A1 (de) 2000-11-30 2002-06-06 Bosch Gmbh Robert Hubgesteuertes Ventil als Kraftstoff-Zumesseinrichtung eines Einspritzsystems für Brennkraftmaschinen
CN100383375C (zh) * 2001-06-02 2008-04-23 彭光斌 电控高压喷油泵
EP1392371B1 (en) 2001-06-08 2006-12-20 Nippon Shokubai Co., Ltd. Water-absorbing agent, its production and sanitary material
DE10134535A1 (de) * 2001-07-16 2002-09-19 Bosch Gmbh Robert Druckausgeglichenes I-Ventil für eine fluidfördernde Hochdruckpumpe
DE10252547B4 (de) * 2002-11-08 2014-12-24 Robert Bosch Gmbh Druckausgeglichenes, direktgesteuertes Ventil
DE10331188B4 (de) * 2003-07-10 2006-07-20 Man B & W Diesel Ag Motor
DE102004013244A1 (de) * 2004-03-18 2005-10-06 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
CN100424333C (zh) * 2006-01-29 2008-10-08 西南大学 转盘分层变量可调组合式燃油喷射系统
CN100398800C (zh) * 2006-03-09 2008-07-02 西南大学 集成式燃油分层变量喷射装置
JP2007255328A (ja) * 2006-03-23 2007-10-04 Toyota Motor Corp 噴射燃料増圧装置
JP4678064B2 (ja) * 2008-12-26 2011-04-27 株式会社デンソー 高圧ポンプ
CN101806264B (zh) * 2009-02-12 2011-10-19 南京威孚金宁有限公司 新型电控分配泵
CN103244328B (zh) * 2012-06-20 2016-06-08 南京威孚金宁有限公司 调压正时提前装置
CN102943726A (zh) * 2012-10-22 2013-02-27 安徽中鼎动力有限公司 一种设有分配泵的燃油喷射系统及包括该系统的柴油机
HUE060337T2 (hu) * 2017-06-29 2023-02-28 Kaercher Alfred Se & Co Kg Nagynyomású tisztítókészülék

Family Cites Families (13)

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Publication number Priority date Publication date Assignee Title
GB1252437A (ja) * 1968-02-07 1971-11-03
DE2638736C3 (de) * 1976-08-27 1979-02-08 Guenter 8882 Lauingen Stein Kraftstoffeinspritzpumpe für Brennkraftmaschinen mit hydraulischem Regler
US4453896A (en) * 1980-12-17 1984-06-12 The Bendix Corporation Distributor pump with floating piston single control valve
US4573442A (en) * 1982-06-10 1986-03-04 Nippondenso Co., Ltd. Fuel injection pump having a compact spill-port timing control unit
JPS5965523A (ja) * 1982-10-05 1984-04-13 Nippon Denso Co Ltd 燃料噴射装置
JPS5968554A (ja) * 1982-10-14 1984-04-18 Nissan Motor Co Ltd デイ−ゼルエンジンの燃料噴射ポンプ
DE3412834A1 (de) * 1984-04-05 1985-10-24 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzpumpe
US4671239A (en) * 1984-07-17 1987-06-09 Nippondenso Co., Ltd. Fuel injection pump
JPH0692743B2 (ja) * 1985-04-01 1994-11-16 日本電装株式会社 流体制御用電磁弁
DE3719832A1 (de) * 1987-06-13 1988-12-22 Bosch Gmbh Robert Kraftstoffeinspritzpumpe
US5215060A (en) * 1991-07-16 1993-06-01 Stanadyne Automotive Corp. Fuel system for rotary distributor fuel injection pump
DE4238727C2 (de) * 1992-11-17 2001-09-20 Bosch Gmbh Robert Magnetventil
DE4323683A1 (de) * 1993-07-15 1995-01-19 Bosch Gmbh Robert Kraftstoffeinspritzpumpe

Also Published As

Publication number Publication date
WO1998049441A1 (de) 1998-11-05
DE59804123D1 (de) 2002-06-20
CN1083935C (zh) 2002-05-01
EP0910738A1 (de) 1999-04-28
JP2000513784A (ja) 2000-10-17
US6280160B1 (en) 2001-08-28
CN1222953A (zh) 1999-07-14
DE19717494A1 (de) 1998-10-29

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