EP0163078B1 - Soupape de refoulement - Google Patents

Soupape de refoulement Download PDF

Info

Publication number
EP0163078B1
EP0163078B1 EP85104323A EP85104323A EP0163078B1 EP 0163078 B1 EP0163078 B1 EP 0163078B1 EP 85104323 A EP85104323 A EP 85104323A EP 85104323 A EP85104323 A EP 85104323A EP 0163078 B1 EP0163078 B1 EP 0163078B1
Authority
EP
European Patent Office
Prior art keywords
valve
delivery
closing member
injection
pressure
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
Application number
EP85104323A
Other languages
German (de)
English (en)
Other versions
EP0163078A1 (fr
Inventor
Peter Dipl.-Math. Wannenwetsch
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 EP0163078A1 publication Critical patent/EP0163078A1/fr
Application granted granted Critical
Publication of EP0163078B1 publication Critical patent/EP0163078B1/fr
Expired legal-status Critical Current

Links

Images

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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7772—One head and seat carried by head of another
    • Y10T137/7774—Supporting valve spring carried by supporting valve

Definitions

  • the invention is based on a pressure valve according to the preamble of the main claim.
  • a pressure valve known from CH-PS-394 710
  • the so-called dripping or re-injection of fuel after the effective delivery stroke of the injection pump piston is to be prevented by providing a return suction collar on the pressure valve in combination with a relief throttle, optionally controlled by a pressure-maintaining valve .
  • pressure waves would occur in the fuel supply line between the pressure valve and the injection valve, which would reciprocate between the injection valve and the pressure valve.
  • the returning waves reflected from the pressure valve to the injection valve can subsequently open it, so that fuel leaks occur with the known disadvantages.
  • the known configuration has only the purpose of preventing the injection or dripping, namely in a wide range of the injection quantity control per injection stroke.
  • the relief throttle which is not controlled by a pressure control valve, has the effect that the residual pressure in the fuel delivery line changes greatly with the speed.
  • the delivery line between the pressure valve and the injection valve is relieved in the same way as with large injection quantities.
  • a more or less large swallowing volume is effective, which has to be filled up by the pump piston delivery until the injection pressure at the injection valve is reached.
  • this disadvantageously leads to noticeable quantity spreads due to the different residual pressures, which have a disadvantageous effect on the running behavior of the internal combustion engine.
  • part of the useful stroke of the pump piston is lost.
  • a cylinder fitted into the passage channel of the valve body is provided as the guide part of the pressure valve closing element.
  • the fuel delivery with the pressure valve open then takes place via the axial relief channel upstream of the throttle and a transverse channel which connects the relief channel to an annular groove separating the suction collar from the guide part.
  • relief of the spring chamber is only possible via the relief channel which extends coaxially through the entire valve closing member.
  • the throttle connection on the valve closing member of the pressure valve is then intended to prevent the valve closing member from lifting during ignition fuel injection by the amount which corresponds to the relief volume without the throttle. This is to prevent the fuel delivery line from being relieved by the full amount of the relief volume made available by the relief association at the end of the spray. This relief would lead to an unsatisfactory operating result.
  • the throttle connection is intended to switch off the discharge completely in the operating range in which ignition fuel is to be injected, in that the amount of ignition fuel flows past the relief collar via the throttle connection without any noticeable pressure drops. In the case of pure liquid power operation, on the other hand, the relief provided by the return suction collar should take full effect.
  • a pressure valve is also known from FR-A-1 050 441, in which a check valve is integrated.
  • this pressure valve has no closing element which has a continuous relief channel.
  • the check valve of this known pressure valve closes a channel leading to the injection side and is connected on the valve spring side to a pressure chamber which is enclosed between a head and a suction collar of the pressure valve closing member in the through channel of the pressure valve.
  • the head in this known pressure valve closing member has a cylindrical part which, in the closed state, lies within a cylindrical bore which is enlarged compared to the diameter of the valve seat.
  • the cylindrical part has an annular gap with the cylindrical bore or it is tightly fitted.
  • the delivery rate is increased briefly at the start of delivery in such a way that a pre-injection occurs, which is terminated when the cylindrical part of the pressure valve closing member emerges from the cylindrical bore and the remaining part has to be filled up to the prevailing pressure level.
  • the check valve has the task that the opening movement is not impeded even when there is sufficient play between the cylindrical part and the cylindrical bore. When the valve is opened, the check valve can be used to equalize the pressure in the enclosed space.
  • this pressure valve and the other proposed solutions according to FR-A-1 050 441 serve the purpose of achieving a damped closing movement of the valve closing element, in order to reduce pressure waves in the injection line after the end of delivery, in addition to the volume relief by means of a suction collar, instead of as in the case of the Pressure valve according to CH-A-394 710 to use a check valve, serving as a constant pressure valve.
  • the pressure in the delivery line cannot generally be limited to a maximum value.
  • the actual stroke of the valve corresponds in all cases in which the damping device is relieved to the injection valve to the delivered fuel injection quantity.
  • the delivery line is relieved of relatively high loads with small injection quantities analogous to the relief for larger injection quantities.
  • the pressure valve according to the invention with the characterizing features of the main claim has the advantage that the pressure in the delivery line is generally limited to a maximum value by the check valve, which is less than the opening pressure of the fuel injector, so that no post-injection can occur.
  • the configuration of the return suction collar ensures that, with small injection quantities or with a low delivery rate of the fuel delivered from the pump work chamber to the injection valve, the fuel can flow over the throttle connection without the valve closing member of the pressure valve being lifted substantially from its seat.
  • the relief stroke or the effect of the relief collar when the pressure valve is closed is then correspondingly small, so that a relatively high residual pressure remains in the delivery line. So that this residual pressure does not exceed the opening pressure of the injection valves, the effect of the check valve is essential here.
  • the throttling effect of the throttle connection increases in such a way that fuel quantities influencing the movement of the closing element of the pressure valve hardly overflow here.
  • the return suction collar thus comes into full effect in such a way that the effect of the check valve is no longer of fundamental importance for maintaining a residual pressure below the nozzle opening pressure.
  • the pump piston delivers a uniformly long delivery phase. This is particularly important when the internal combustion engine is operated with a so-called quiet running device, as already mentioned.
  • the fuel delivery should also be used with the effective delivery stroke of the pump piston. This also applies in particular to the critical range of idling and the low load and is achieved by the high residual pressure that can be achieved with the device according to the invention. A useful stroke loss, which is particularly disadvantageous for idle operation, is also avoided.
  • the requirements can be met in all operating areas of an internal combustion engine, which is operated in particular with a silent running device, and the working capacity in relation to the useful stroke of the fuel supply device can be optimally utilized.
  • the residual pressure in the delivery line which can be controlled with the pressure valve according to the invention, can be used to influence the duration of the spray at a given cross section of the injection nozzle.
  • the figure shows a longitudinal section through a pressure valve 1, which is screwed into the housing 2 of a fuel injection pump, not shown, which is constructed, for example, according to DE-OS-2 353 737.
  • the pressure valve 1 has a connecting piece 4, which has an external thread 5 at one end and is screwed with this into a threaded bore 6 in the housing 2.
  • a delivery line 7 coaxially opens into the threaded bore from the pump work chamber of the fuel injection pump (not shown). This has a connection via the pressure valve 1 to a further delivery line 7 ', to the end of which an injection valve 8 is connected.
  • the connecting piece 4 is constructed essentially cylindrical and has an axial cylindrical recess 9 which is open towards the screw-in side. Coaxial to the cylindrical recess 9 there is a connection bore 11 which opens into a connection nipple 12 of the connection piece and connects the recess 9 to the delivery line 7 'or the injection valve 8.
  • a tubular valve seat body 14 is inserted into the axial recess 9, which has a collar 15 at its end, at the end of the pump work space, by means of which it is held by the end 16 of the connecting piece from the shoulder 17 on the bottom of the threaded bore 6.
  • the tubular valve seat body 14 has a valve seat 19 on which a conical sealing surface 20 of a valve closing member 21 of the pressure valve comes to rest.
  • the valve closing member has, in a known manner, wing-shaped guide surfaces 23 which are guided in the axial bore 24 of the valve seat body 14 and between which fuel can pass to the valve seat.
  • the valve closing member is designed as a cylinder 25, which is significantly reduced in diameter compared to the diameter of the bore 24.
  • the valve closing member has a collar 26 which is fitted into the bore 24 of the valve seat body.
  • the collar 26 On its outer circumference, the collar 26 has a bevel 27 which produces a throttle connection between the part of the cylinder 25 on the guide surface side and the part on the sealing surface side.
  • the valve closing member 21 also has coaxially a relief channel 28 which on the one hand has an outlet 30 on the part of the cylinder 25 on the guide surface side and on the other hand opens centrally on the end face of a pin 31. This sits on an end face 32 of the valve closing member, which adjoins the sealing surface 20 and that Valve closing member limited to the interior of the recess 9.
  • the pin 31 serves to center a cup-shaped part 34, the cylindrical wall of which merges into an outer collar 35 which is placed flush on the end face 32.
  • the pin 31 protrudes into the cylindrical interior 36 of the cup-shaped part 34.
  • On the outer collar 35 is a closing spring 37, which on the other hand is supported on the end face 38 of the recess 9 and holds the cup-shaped part 34 in a positive connection with the valve closing member 21 and endeavors to keep this with its sealing surface 20 on the valve seat 19.
  • the cup-shaped part 34 can also be connected to the valve closing member in some other way. B. also serve a weld.
  • a check valve 46 is provided with a closing spring 40, which is supported on the one hand on the end face of the pin 31 and on the other hand acts on a valve plate 41 which serves to guide a spherical valve closing member 42.
  • This has a seat in a conical recess 43 at the bottom of the pot-shaped part, this recess merging into a throttle 44 which opens into the spring chamber 45 of the recess 9 receiving the pressure valve closing spring 37.
  • valve closing member 21 is raised under the influence of the pressure of the fuel supplied via the delivery line 7, as shown in the figure. If only a small amount of fuel is pumped per unit of time, this can flow past the bevel 27 through the throttle connection without the collar 26 having to be completely removed from the bore 24.
  • the valve is only raised slightly, as shown in the drawing, and yet a pressure builds up in the delivery line 7 ′, which is above the opening pressure of the injection valve 8 and causes an injection. At the end of the delivery stroke, the pressure collapses on the pump side, so that the valve closing member 21 is brought into the closed position under the action of the valve closing spring 37.
  • the collar 26, which is also referred to as a suck-back collar, draws fuel back from the area upstream of the valve seat 19 in accordance with its previous stroke until the valve closing member comes into the closed position.
  • the amount of suckback is reduced by the amount of fuel that flows as a compensating flow through the throttle connection 27 during this movement. In this way, the fuel is relieved in the delivery line between the valve closing member and the injection valve 8 in a known manner.
  • pressure waves run in a known manner through the delivery line 7 due to the dynamic conditions, which are reflected on the valve closing member 21 and run back and forth between the injection valve and valve closing member.
  • These pressure waves can reach pressure values that are higher than the opening pressure of the injection valve, so that fuel can be re-injected without additional measures, as already described at the beginning.
  • the average pressure in the delivery line is then still greater than the closing pressure of the injection valve due to the dynamic pressure conditions.
  • the peak pressures of the pressure waves are higher, the higher the total residual pressure in the delivery line 7 'after the Ventitschtiessgtieds 21 has been shot.
  • a check valve 46 creates a connection from the spring chamber 45 or the delivery line 7 ′ to the delivery line 7 on the pump work chamber side beyond the valve closing member 21 when the opening pressure of this check valve is exceeded.
  • a certain amount of fuel can flow away via the throttle 44, which causes a reduction of the pressure wave that has arrived.
  • the wave then reflected towards the injection valve has pressure values that are not above the opening pressure of the injection valve.
  • the throttle influence of the throttle connection 27 increases in such a way that the suckback collar 26 emerges from the bore 24 and the delivered fuel can flow unthrottled past the suckback collar into the spring chamber 45.
  • the full valve closing member stroke is effective for sucking back fuel quantities.
  • the relief association essentially takes over the relief of the injection line to prevent post-injection alone.
  • the amount of relief is then essentially a relief volume of the valve stroke x free ring area of the end face of the relief collar 26. Furthermore, during the rapid stroke movement of the valve closing member, no substantial compensation amounts flow past the throttle connection 27, so that the delivery line is maximally relieved.
  • the throttle connection 27 on the return suction collar can also be produced with the aid of an increased play between collar 26 and bore 24 or through bores in the collar itself.
  • the closing member 21 would first have to carry out the full stroke, which corresponds to the relief stroke; until the connection from the conveyor line 7 to the conveyor line 7 'is established.
  • the low delivery rate would result in a delayed injection point.
  • the delivery line 7 ' would be relieved in particular in the same way as the closing member, as is the case with partial load or full load or with high delivery rates. This relief corresponds to a swallowing volume which is high for a low delivery rate during idling operation and which has to be filled up until a pressure is reached in the delivery line 7 'which corresponds to the opening pressure of the injection valve.
  • a spray delay would also occur here and a correspondingly long pre-delivery stroke would be required for the pump piston.
  • This long pre-delivery stroke which due to the low delivery rate achieved by the silent running device is even greater than in normal operation without a silent running device, makes it necessary for the injection pump to provide a relatively large useful stroke, the stroke which is effective for fuel delivery to the fuel injection nozzle got to.
  • this useful stroke for idling is lost to the useful stroke in the rest of the load range. This complicates the use of a silent running device to a considerable extent or requires a complex pump design with a high useful stroke.
  • the delivery line 7 ' is relieved only slightly at low delivery rates, particularly in the area of quiet operation.
  • the check valve 46 is provided, via which the pressure peaks are reduced in this operating range by fuel being throttled by the throttle 44 when the check valve is open, the interior 36 and the relief channel 35 can flow back to the pump work space via the outlet 30.
  • a desired residual pressure can be maintained in the various operating areas of the internal combustion engine in the delivery line 7 'without the opening pressure of the injection nozzles being exceeded after they are closed .
  • the opening pressure of the check valve is advantageously chosen so that it is approximately as large as the injection valve closing pressure. This means that a very high stand pressure or residual pressure in the delivery line can be maintained with the lowest absorption volume.
  • long spray times are obtained in idle-quiet operation, without these being as large as with a pressure valve which has no check valve. In this case, very high residual pressures would remain in the delivery lines 7 'because of the throttle connection 27 and thus very long spraying times would occur, some of which would be extended by post-spraying.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Check Valves (AREA)

Claims (8)

1. Soupape de refoulement pour le montage dans une conduite de refoulement (7, 7') entre une enceinte de travail de pompe d'une pompe d'injection de carburant et le point d'injection au moteur à combustion interne alimenté par la pompe d'injection de carburant, avec un corps de siège de soupape (14), pourvue d'un siège de soupape (19), qui possède un canal traversant (24), dans lequel est guidé un organe d'obturation de soupape de refoulement (21), qui est disposé entre siège de soupape (19) et un ressort de pression (37), qui s'appuie en un point fixe dans une enceinte de ressort (45) et qui possède une surface d'étanchéité (20), qui travaille ensemble avec le siège de soupape (19), avec une collerette d'aspiration de retour (26), se trouvant sur le côté de l'enceinte de travail de pompe de la surface d'étanchéité, immergée dans le canal traversant (24) à l'organe d'obturation de soupape de refoulement se trouvant en position de fermeture et possède un canal de décharge (28) pourvu d'un étranglement (44), au travers duquel le canal traversant (24) est reliable au côté de l'enceinte de travail de pompe de la collerette d'aspiration de retour (26) avec l'enceinte de ressort (45) et est obturable du côté enceinte de travail de pompe d'étranglement (44), par un organe d'obturation (42) d'une soupape anti-retour (46), qui possède un ressort de fermeture (40), s'appuyant à l'organe d'obturation de soupape, caractérisée en ce que la collerette d'aspiration de retour (26) possède une liaison d'étranglement (27), qui relie l'enceinte limitrophe à la collerette d'aspiration de retour et qui se trouve côté surface d'étanchéité, avec une partie limitrophe du canal traversant (24), faisant guidage et sans étranglement vers l'enceinte de travail de pompe.
2. Soupape de refoulement selon la revendication 1, caractérisée en ce que la liaison d'étranglement (27) est formée d'un aplatissement au diamètre extérieur de la collerette d'aspiration de retour (26).
3. Soupape de refoulement selon la revendication 1 ou 2, caractérisée en ce que l'organe d'obturation de la soupape de refoulement (21) possède une face annulaire frontale (32) côté enceinte à ressort, avec un tourillon axial (31) et qu'une partie en forme de pot (34) est appliquée sur cette face annulaire frontale, avec une collerette extérieure (35), sur laquelle vient en appui le ressort de pression (37) de l'organe d'obturation de soupape (21) et qu'une enceinte intérieure (36) incluse par la partie en forme de pot est reliée au canal de décharge (28) et qui contient la soupape anti- retour (46) dont l'organe d'obturation (42) commande un alésage d'étranglement (44), conduisant au travers de la paroi de la partie en forme de pot.
4. Soupape de refoulement selon la revendication 3, caractérisée en ce que l'alésage d'étranglement (44) est disposé dans le fond de la partie en forme de pot.
5. Soupape de refoulement selon la revendication 4, caractérisée en ce que l'alésage d'étranglement (44) s'étend en forme de diffuseur sur le côté intérieur du fond et en formant un siège de soupape (43) de l'organe d'obturation (42) de la soupape antiretour, dont le ressort de fermeture (40) s'appuie au tourillon (31
6. Soupape de refoulement selon la revendication 3, caractérisée en ce que l'organe d'obturation de la soupape anti-retour est une sphère, qui est guidée dans un plateau de soupape (41).
7. Soupape de refoulement selon l'une des revendications précédentes, caractérisée en ce que la soupape de refoulement est appliquée à une pompe d'injection de carburant, dont le taux de refoulement de carburant est réduit dans une certaine zone de fonctionnement, par prélèvement d'un débit partiel du débit de carburant refoulé par le piston de pompe, lors de sa course de refoulement.
8. Soupape de refoulement selon l'une des revendications 1 ou 2, caractérisée en ce que la pression d'ouverture de la soupape anti-retour (46) est à peu près de même importance que la pression de fermeture de la soupape d'injection (8).
EP85104323A 1984-05-10 1985-04-10 Soupape de refoulement Expired EP0163078B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843417210 DE3417210A1 (de) 1984-05-10 1984-05-10 Druckventil
DE3417210 1984-05-10

Publications (2)

Publication Number Publication Date
EP0163078A1 EP0163078A1 (fr) 1985-12-04
EP0163078B1 true EP0163078B1 (fr) 1988-06-29

Family

ID=6235383

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85104323A Expired EP0163078B1 (fr) 1984-05-10 1985-04-10 Soupape de refoulement

Country Status (7)

Country Link
US (1) US4648369A (fr)
EP (1) EP0163078B1 (fr)
JP (1) JPS60247049A (fr)
KR (1) KR930010661B1 (fr)
BR (1) BR8502199A (fr)
DE (2) DE3417210A1 (fr)
SU (1) SU1489583A3 (fr)

Families Citing this family (56)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61138875A (ja) * 1984-12-12 1986-06-26 Nissan Motor Co Ltd 燃料噴射装置の燃料吐出弁
JPS62169256U (fr) * 1986-04-17 1987-10-27
GB8725029D0 (en) * 1986-11-27 1987-12-02 Daimler Benz Ag Inclined-edge controlled fuel injection pump
DE3704743A1 (de) * 1987-02-14 1988-08-25 Schaeffler Waelzlager Kg Steuereinrichtung fuer ein ventil
JPS63151972U (fr) * 1987-03-27 1988-10-05
ES2035324T3 (es) * 1988-01-16 1993-04-16 Lucas Industries Public Limited Company Valvula de control de presion.
EP0325211B1 (fr) * 1988-01-18 1994-06-22 Diesel Kiki Co., Ltd. Soupape d'équilibrage de pression
DE3843819A1 (de) * 1988-09-09 1990-03-22 Bosch Gmbh Robert Druckventil
JP2969635B2 (ja) * 1988-12-16 1999-11-02 株式会社デンソー 燃料噴射ポンプ
BR9007008A (pt) * 1989-11-13 1992-03-17 Bosch Gmbh Robert Valvula de pressao
JPH04121456A (ja) * 1990-09-12 1992-04-22 Nissan Motor Co Ltd 直噴式ディーゼルエンジン
GB9302566D0 (en) * 1993-02-10 1993-03-24 Lucas Ind Plc Valve
US5477829A (en) * 1994-08-08 1995-12-26 Ford Motor Company Automotive returnless fuel system pressure valve
US5582202A (en) * 1994-12-21 1996-12-10 Bridge Products, Inc. Air conditioner system charge/relief valve
US5546981A (en) * 1995-01-12 1996-08-20 Gilbarco, Inc. Check valve
DE19535368C2 (de) * 1995-09-25 1998-04-30 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung für Brennkraftmaschinen
DE19645643A1 (de) * 1996-11-06 1998-05-07 Braun Ag Überdruckventil für eine Munddusche
DE19706591A1 (de) * 1997-02-20 1998-08-27 Bosch Gmbh Robert Druckventil
JP2001263187A (ja) * 2000-03-17 2001-09-26 Denso Corp エンジン用燃料供給装置のチェックバルブ
JP4140175B2 (ja) * 2000-07-21 2008-08-27 株式会社デンソー 内燃機関用蓄圧式燃料噴射装置
KR100384299B1 (ko) * 2000-11-27 2003-05-16 현대자동차주식회사 연료맥동음 저감장치
DE10146113A1 (de) * 2001-09-19 2003-04-03 Sms Demag Ag Spritzbalken für eine hydraulische Entzunderungsanlage
US6988488B2 (en) * 2003-04-15 2006-01-24 Visteon Global Technologies, Inc. Fuel pressure relief valve
US7028708B1 (en) 2003-05-09 2006-04-18 Hydro-Gear Limited Partnership Combined check valve and pressure relief valve
US7007708B2 (en) * 2003-10-17 2006-03-07 Delphi Techonologies, Inc. Flow control valve
US7296594B1 (en) 2005-03-22 2007-11-20 Hydro-Gear Limited Partnership Combination check valve and neutral valve assembly for use in a hydraulic component
JP4453028B2 (ja) * 2005-03-30 2010-04-21 株式会社デンソー 高圧燃料ポンプ
CN100473821C (zh) * 2005-03-30 2009-04-01 株式会社电装 具有柱塞的燃油泵及使用这种燃油泵的燃油供应系统
US7451780B1 (en) 2005-05-16 2008-11-18 Hydro-Gear Limited Partnership Multifunction valve for use in a hydraulic component
EP1891360B1 (fr) * 2005-06-16 2014-10-01 Raval A.C.S. LTD Vanne a clapet double pour un systeme de carburant
JP4380739B2 (ja) * 2007-07-06 2009-12-09 株式会社デンソー 高圧燃料ポンプ
US7628140B2 (en) * 2007-09-27 2009-12-08 Caterpillar Inc. High-pressure pump or injector plug or guide with decoupled sealing land
JP4595996B2 (ja) * 2007-11-16 2010-12-08 トヨタ自動車株式会社 内燃機関の高圧燃料供給装置
US20100257916A1 (en) * 2008-03-27 2010-10-14 Ip Innovative Products, Llc Accuracy enhancing valve assembly and related method of use
WO2010064475A1 (fr) * 2008-12-02 2010-06-10 株式会社パイオラックス Clapet antiretour
JP4775488B2 (ja) * 2009-11-30 2011-09-21 トヨタ自動車株式会社 内燃機関の高圧燃料供給装置
US8132558B2 (en) * 2009-12-01 2012-03-13 Stanadyne Corporation Common rail fuel pump with combined discharge and overpressure relief valves
JP5051279B2 (ja) * 2009-12-21 2012-10-17 株式会社デンソー 定残圧弁
US8622046B2 (en) 2010-06-25 2014-01-07 Caterpillar Inc. Fuel system having accumulators and flow limiters
JP2012172749A (ja) * 2011-02-21 2012-09-10 Fuji Koki Corp バルブ装置
EP2495431B1 (fr) * 2011-03-04 2014-01-15 OMT Officine Meccaniche Torino S.p.A. Pompe hydraulique en particulier pompe à carburant
JP5501272B2 (ja) * 2011-03-08 2014-05-21 日立オートモティブシステムズ株式会社 高圧燃料供給ポンプ
US9097356B2 (en) * 2011-09-01 2015-08-04 Piolax Inc. Check valve
WO2013067190A2 (fr) * 2011-11-01 2013-05-10 Cummins Inc. Injecteur de combustible doté d'un ensemble soupape de commande d'injection
JP5920636B2 (ja) * 2013-09-13 2016-05-18 株式会社デンソー 高圧ポンプ
JP1546565S (fr) * 2015-08-19 2016-03-28
US20180223817A1 (en) * 2017-02-03 2018-08-09 Peopleflo Manufacturing, Inc. Reciprocating Pump Having a Combination Check Valve and Relief Valve
CN109139831A (zh) 2017-06-15 2019-01-04 博格华纳公司 带有刚度可控止回阀的张紧器
JP6747482B2 (ja) * 2017-09-29 2020-08-26 株式会社デンソー 高圧ポンプ
WO2019065992A1 (fr) * 2017-09-29 2019-04-04 株式会社デンソー Pompe haute pression
CN111656051B (zh) 2018-02-26 2023-09-29 博格华纳公司 具有内部储存器技术主孔的可变力张紧器
CN109708347A (zh) * 2018-10-12 2019-05-03 青岛海尔股份有限公司 制冰机的供水装置及具有其的制冰机和冰箱
JP2020101279A (ja) 2018-12-21 2020-07-02 ボーグワーナー インコーポレーテッド 内部チェックバルブを含むピストンが備えられたテンショナ
HUP1900114A1 (hu) * 2019-04-05 2020-10-28 Kerox Ipari Es Kereskedelmi Kft Vezérelt dugattyús szelep
US11408525B2 (en) * 2020-04-10 2022-08-09 II Peter Stephen Heberling Pressure relief valve for inflatable structures and boats
EP4377592A1 (fr) * 2021-07-29 2024-06-05 Beaconmedaes LLC Clapet antiretour à débit élevé destiné à des applications de gaz médical

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB566957A (en) * 1942-04-01 1945-01-22 Bendix Aviat Corp Improvement in fuel injection apparatus
US2706490A (en) * 1950-01-18 1955-04-19 Nordberg Manufacturing Co Variable retraction valve
FR1050441A (fr) * 1950-11-17 1954-01-07 British Internal Combust Eng Perfectionnements aux dispositifs d'injection de combustible liquide
CH394710A (de) * 1962-08-09 1965-06-30 Schweizerische Lokomotiv Brennstoffeinspritzpumpe für Brennkraftmaschinen
US3309024A (en) * 1965-01-07 1967-03-14 Int Harvester Co Fuel delivery valve and injection apparatus employing same
US3477458A (en) * 1965-01-07 1969-11-11 Int Harvester Co Fuel delivery valve assembly and method
US3479999A (en) * 1967-11-02 1969-11-25 Ulrikh Ulrikhovich Keller Injection pump valve
US3933132A (en) * 1971-10-20 1976-01-20 Isuzu Motors Limited Another liquid-mixing injection system for internal-combustion engine
FR2296104A2 (fr) * 1973-12-13 1976-07-23 Sigma Diesel Perfectionnements apportes aux dispositifs d'injection pour moteur a combustion interne
US3896845A (en) * 1974-06-13 1975-07-29 Gen Motors Corp Accumulator charging and relief valve
JPS5675957A (en) * 1979-11-21 1981-06-23 Diesel Kiki Co Ltd Draft device of delivery valve for fuel injection pump
JPS56115849A (en) * 1980-02-15 1981-09-11 Nippon Denso Co Ltd Fuel injection pump for internal combustion engine
IT1150318B (it) * 1981-03-21 1986-12-10 Bosch Gmbh Robert Pompa di iniezione del carburante per motori endotermici
DE3138211A1 (de) * 1981-09-25 1983-04-07 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoff-einspritzpumpe fuer brennkraftmaschinen

Also Published As

Publication number Publication date
SU1489583A3 (ru) 1989-06-23
DE3563553D1 (en) 1988-08-04
EP0163078A1 (fr) 1985-12-04
DE3417210A1 (de) 1985-11-14
KR850008704A (ko) 1985-12-21
KR930010661B1 (ko) 1993-11-05
US4648369A (en) 1987-03-10
BR8502199A (pt) 1986-01-07
JPS60247049A (ja) 1985-12-06

Similar Documents

Publication Publication Date Title
EP0163078B1 (fr) Soupape de refoulement
EP0116168B1 (fr) Pompe d'injection de combustible
DE2803049A1 (de) Pumpe-duese fuer brennkraftmaschinen
DE3521427C2 (fr)
EP0688950B1 (fr) Système d'injection de carburant
DE19939420A1 (de) Kraftstoffeinspritzverfahren und -system für eine Brennkraftmaschine
EP0204982B1 (fr) Dispositif d'injection de combustible pour moteurs à combustion interne
DE3715614A1 (de) Kraftstoffeinspritzpumpe
DE19844891A1 (de) Kraftstoffeinspritzventil für Brennkraftmaschinen
WO2004003377A1 (fr) Dispositif permettant d'amortir la course de l'aiguille sur des injecteurs de carburant commandes par pression
DE1476247A1 (de) Kraftstoffeinspritzvorrichtung fuer mit Kraftstoffeinspritzung und Kompressionszuendung arbeitende Brennkraftmaschinen
DE10117600C1 (de) Hochdruck-Kraftstoffpumpe für ein Kraftstoffsystem einer direkteinspritzenden Brennkraftmaschine, Kraftstoffsystem sowie Brennkraftmaschine
EP1045975B1 (fr) Unite servant a commander l'etablissement de la pression dans une unite de pompage
DE3401658C2 (fr)
DE4106813A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE3844133C2 (fr)
DE3150675C2 (de) Zündvorrichtung für eine gemischverdichtende selbstzündende Brennkraftmaschine
DE2509068C2 (fr)
DE19812170A1 (de) Kraftstoffeinspritzanlage für eine mehrzylindrige Brennkraftmaschine
DE3524241A1 (de) Kraftstoffeinspritzpumpe fuer brennkraftmaschinen
DE10023960A1 (de) Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine
AT397129B (de) Kraftstoffeinspritzdüse
DE2658833C2 (fr)
DE916605C (de) Verfahren einer in Vor- und Haupteinspritzung unterteilten Kraftstoffeinspritzung mittels Einspritzpumpe
EP0610584A1 (fr) Dispositif d'injection de combustible à pré-injection et injection principale de combustibles différents par un injecteur mono-aiguille

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19850410

AK Designated contracting states

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19860911

D17Q First examination report despatched (deleted)
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3563553

Country of ref document: DE

Date of ref document: 19880804

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19930405

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19930429

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19930624

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19940410

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19940410

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19941229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19950103

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST