EP1658438A1 - Pompe a liquides - Google Patents

Pompe a liquides

Info

Publication number
EP1658438A1
EP1658438A1 EP04762564A EP04762564A EP1658438A1 EP 1658438 A1 EP1658438 A1 EP 1658438A1 EP 04762564 A EP04762564 A EP 04762564A EP 04762564 A EP04762564 A EP 04762564A EP 1658438 A1 EP1658438 A1 EP 1658438A1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure chamber
valve piston
chamber
liquid pump
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
EP04762564A
Other languages
German (de)
English (en)
Other versions
EP1658438B1 (fr
Inventor
Stanislaw Bodzak
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 EP1658438A1 publication Critical patent/EP1658438A1/fr
Application granted granted Critical
Publication of EP1658438B1 publication Critical patent/EP1658438B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • F04C14/265—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels being obtained by displacing a lateral sealing face
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011—Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023—Valves in the fuel supply and return system
    • F02M37/0029—Pressure regulator in the low pressure fuel system
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047—Layout or arrangement of systems for feeding fuel
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/041—Arrangements for driving gear-type pumps
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/22—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system
    • F02M37/32—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system characterised by filters or filter arrangements
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/22—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system
    • F02M37/32—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system characterised by filters or filter arrangements
    • F02M37/44—Filters structurally associated with pumps
    • 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
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/22—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system
    • F02M37/54—Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines, e.g. arrangements in the feeding system characterised by air purging means

Definitions

  • the invention is based on a liquid pump according to the preamble of claim 1.
  • Such a liquid pump designed as a gear pump is known from DE 196 25 564 AI.
  • This gear pump is provided for a fuel injection device of an internal combustion engine and has a housing in which a pump chamber is formed. A rotatingly driven pair of gear wheels meshing with one another on their outer circumference is arranged in the pump chamber.
  • the gearwheels require fuel as the delivery medium from a suction space connected to a storage tank along the delivery channels formed between the circumference of the gearwheels and the circumferential walls of the pump chamber into a pressure chamber.
  • the gear pump also has a pressure relief valve to limit the pressure in the pressure chamber. If a predetermined pressure in the pressure chamber is exceeded, the pressure relief valve opens a connection channel of the pressure chamber to the intake chamber.
  • the pressure relief valve has a valve piston which is guided in a bore in a plane perpendicular to the axes of rotation of the gear wheels and which cooperates with a valve seat.
  • the valve piston can be moved against the force of a prestressed spring.
  • the pressure relief valve enables pressure limitation at the pressure generated by the gear pump and thus a limitation of the required fuel quantity.
  • a filter through which the sucked-in liquid flows or a filter is usually connected upstream of the liquid pump downstream, through which the required liquid flows. Depending on the degree of contamination of the filter, the liquid pump requires a different amount of liquid, which cannot be compensated by the pressure relief valve.
  • the liquid pump according to the invention with the features according to claim 1 has the advantage that, in addition to limiting the delivery pressure, the delivery rate is also regulated, so that the delivery rate is set independently of the degree of contamination of the filter. This is done in a simple manner by varying the force acting on the valve piston in the closing direction depending on the pressure downstream after the filter.
  • the function of the demand control is achieved in a simple manner by the design according to claim 2.
  • the design according to claim 5 allows a simple structure of the pressure relief valve. Due to the design according to claim 6, the connecting channel is formed in a simple manner. Due to the design according to claim 9, when the valve piston moves in the bore, the conveying medium can be displaced from the room or flow into it.
  • FIG. 1 shows a gear pump in a section along line II in FIG. 2
  • FIG. 2 shows the gear pump in a section along line II-II in FIG. 1
  • FIG. 3 shows the gear pump schematically in a section along line III-III in FIG. 2 in an enlarged view Presentation.
  • a liquid pump shown in FIGS. 1 to 3 is designed as a gear pump and is arranged in a delivery line (not shown) from a storage tank to a high-pressure fuel pump or a fuel injection pump of a fuel injection device of an internal combustion engine, for example of a motor vehicle.
  • the internal combustion engine is a self-igniting internal combustion engine and the fuel that is required by the gear pump is diesel fuel.
  • the gear pump has a multi-part housing which has a housing part 10 and a cover part 12.
  • a pump chamber 14 is formed between the housing part 10 and the cover part 12, in which a pair of gear wheels 16, 18 meshing with one another on their outer circumference is arranged.
  • the housing part 10 has two depressions 20, 22 to form the pump chamber 14, from the bottom of which a bearing journal 24, 26 projects.
  • the bearing pins 24, 26 are formed in one piece with the housing part 10 and run at least approximately parallel to one another.
  • the bearing pins 24, 26 can be at least partially hollow to reduce the weight of the housing part 10.
  • the gear wheel 16 has a bore 17, via which it is rotatably mounted on the journal 24.
  • the gear wheel 18 has a bore 19, via which it is rotatably mounted on the bearing journal 26.
  • the bearing pins 24, 26 each determined an axis of rotation 25, 27 for the gear wheels 16, 18.
  • the cover part 12 is firmly connected to the housing part 10, for example by means of several Screws.
  • the housing part 10 and the cover part 12 are preferably made of light metal, in particular aluminum.
  • the gear wheels 16, 18 are preferably made of steel, in particular of sintered steel.
  • the gear pump has a drive shaft 30 which is rotatably mounted in the housing part 10.
  • the drive shaft 30 is arranged at least approximately coaxially to the bearing journal 24, the housing part 10 having a bore which continues in the bearing journal 24 and through which the end of the drive shaft 30 passes.
  • a shaft sealing ring is installed between the bore and the drive shaft 30 in order to seal the housing part 10.
  • the drive shaft 30 is coupled to the gear 16, for example via a coupling member 36 arranged between the front end of the bearing journal 24 and the cover part 12.
  • the gear 16 is driven in rotation during operation of the gear pump via the drive shaft 30 and transmits this rotary movement via a spur gear to the also provided with spur gear teeth, which mesh with the gear 16 on its outer circumference.
  • the gear wheels 16, 18 divide the pump chamber 14 by their tooth engagement into two partial areas, of which a first partial area forms a suction chamber 40 and a second partial area forms a pressure chamber 42 ,
  • the suction chamber 40 is in each case between the tooth grooves on the
  • the suction chamber 40 and the pressure chamber 42 each have a connection opening in the wall of the housing part 10 or the cover part 12, via which the suction chamber 40 with a suction line (not shown) from the storage tank and the pressure chamber 42 via a delivery line (also not shown) with the suction chamber of the high-pressure fuel pump or the fuel injection pump is connected.
  • the connection opening in the suction space 40 forms an inlet opening 46 and Connection opening in the pressure chamber 42 forms an outlet opening 48.
  • the gear pump has a pressure relief valve 50 which is arranged in the housing, for example in the housing part 10.
  • a groove 52 is introduced, which extends between the pressure chamber 42 and the suction chamber 40.
  • the groove 52 has a length 1, a width b and a depth t.
  • the groove 52 extends as shown in FIG. 3 when viewed in the direction of the axes of rotation 25, 27 of the toothed wheels 24, 26 viewed approximately tangentially to the toothed wheels 16, 18 and their length 1 is dimensioned such that the groove 52 over the cutting lines 54 of the tip circles Dk the gear 16.18 extends.
  • the groove 52 When viewed in the direction of the axes of rotation 25, 27 of the toothed wheels 16, 18, the groove 52 is arranged at least approximately centrally between the toothed wheels 16, 18.
  • the groove 52 thus forms a connecting channel extending from the pressure chamber 42 to the suction chamber 40.
  • the housing part 10 delimits the pump chamber 14 with a small axial distance from the end faces of the gear wheels 16, 18 with the base of the depressions 20, 22.
  • a bore 56 is made, the diameter d of which is preferably somewhat larger than the width b of the groove 52.
  • the bore 56 runs at least approximately parallel to the axes of rotation 25, 27 of the gear wheels 16, 18 and is preferably related to a connecting line 58 between the axes of rotation 25, 27 of the gear wheels 16, 18 offset by a dimension H from the pressure chamber 42.
  • the dimension H is preferably between about 2 and 5 mm.
  • a valve piston 60 is displaceably guided in the bore 56 as the valve member of the pressure limiting valve 50.
  • the valve piston 60 is clamped between it and the base of the bore 56 by a compression spring 62, for example in the form of a
  • Helical compression spring to the end faces facing it the gear wheel printed 16.18 m.
  • the end faces of the gear wheels 16, 18 are at least approximately flat and at least approximately perpendicular to their axes of rotation 25, 27.
  • the valve piston 60 bears against the end faces of the gear wheels 16, 18 in the region of their tooth engagement.
  • the space 64 defined in the bore 56 by the valve piston 60 on its rear side facing away from the gear wheels 16, 18 is connected to the suction space 40 via a bore 66 in the housing part 10.
  • valve piston 60 is acted upon on part of its end face facing the gear wheels 16, 18 by the pressure prevailing in the pressure chamber 42, by means of which a force directed against the compression spring 62 is generated on the valve piston 60. If the force of the compression spring 62 is greater than the force generated by the pressure prevailing in the pressure chamber 42, the valve piston 60 is in contact with the end faces of the gear wheels 16, 18, which form a valve seat. The passage through the groove 52 and thus the connection between the pressure chamber 42 and the suction chamber 40 is interrupted by the valve piston 60 in cooperation with the gear wheels 16, 18.
  • valve piston 60 If the valve piston 60 is pressed by the force of the compression spring 62 on the end faces of the gear wheels 16, 18, the play of the gear wheels 16, 18 in the pump chamber 14 in the direction of its axis of rotation 25, 27 is reduced, preferably completely eliminated. This is particularly advantageous when starting the gear pump and when starting the internal combustion engine, since the efficiency of the pump is then optimal.
  • the valve piston 60 generates a braking force on the gear wheels 16, 18 due to the friction, which is particularly advantageous when the gear pump starts up, since this results in better flank contact between the teeth of the gear wheels 16, 18. Due to the good efficiency of the gear pump, especially when
  • the gear pump can be dimensioned for a smaller amount than known gear pumps.
  • Valve piston 60 and the position of the valve piston 60 with respect to the pressure chamber 42 and thus the size of the end face of the valve piston 60 acted upon by the pressure prevailing in the pressure chamber 42, the pressure at which the pressure limiting valve 50 opens can be varied.
  • the valve piston 60 With increasing pressure in the pressure chamber 42, the valve piston 60 is displaced further into the bore 56, so that an increasingly larger flow cross section is released by the valve piston 60 in the groove 52.
  • the largest flow cross-section released by the valve piston 60 in the groove 52 is preferably so large that the entire fuel quantity required by the gear wheels 16, 18 can flow back from the pressure chamber 42 into the intake chamber 40 if no fuel may be required by the gear pump.
  • the cross-sectional area of the groove 52 which determines the maximum flow cross-section, is preferably between approximately 30 and 60 mm 2 .
  • the valve piston 60 When the valve piston 60 is immersed in the bore 56, fuel is displaced from the space 64 through the bore 66 into the intake space 40. When the valve piston 60 emerges from the bore 56, the space 64 can be filled again with fuel from the intake space 40 via the bore 66.
  • pressure pulsations occur due to the alternating tooth engagement of the gear wheels 16, 18, and the fuel volume displaced between the teeth in the process.
  • the valve piston 60 bears against the end faces of the toothed wheels 16, 18 in the region of their tooth engagement and is thus acted upon by the pressure prevailing between the toothings. In the event of pressure pulsations between the toothings, the valve piston 60 executes an evasive movement, as a result of which these pressure pulsations are dampened and reduced.
  • the gear pump also has a bypass valve 70, by means of which a connection between the pressure chamber 42 and the suction chamber 40 can be released if the pressure in the pressure chamber 42 is lower than in the suction chamber 40.
  • a bypass valve 70 allows venting and filling of the gear pump.
  • the bypass valve 70 has a valve member 72 which is acted upon by the pressure prevailing in the pressure chamber 42 and is printed by the latter to a valve seat 74 on the housing part 10.
  • the valve member 72 is arranged, for example, in a recess 76 in the groove 52 on its area projecting into the pressure chamber 42.
  • the valve member 72 can be made of an elastomer, for example, and the valve seat 74 can be designed as a flat seat.
  • a bore 78 leads from the valve seat 74 into the space 64 in the bore 56 behind the valve piston 60, which in turn is connected to the intake space 40 via the bore 66.
  • Valve member 72 also engages a closing spring 80, which can be, for example, a prestressed tension spring arranged in the bore 78, which on the one hand engages the valve member 72 and on the other hand is attached to the last turn of the compression spring 62.
  • a closing spring 80 which can be, for example, a prestressed tension spring arranged in the bore 78, which on the one hand engages the valve member 72 and on the other hand is attached to the last turn of the compression spring 62.
  • Closing spring 80 becomes valve member 72 with little force pulled towards the valve seat 74 and thereby reached an abutment on the valve seat 74 when the gear pump is not in operation. If, during operation of the gear pump, the pressure in the pressure chamber 42 is lower than in the suction chamber 40, the bypass valve 70 opens by lifting its valve member 72 from the valve seat 74, so that fuel can get directly from the suction chamber 40 into the pressure chamber 42 and the pressure chamber 42 is filled with fuel. If, during the further operation of the gear pump, the pressure in the pressure chamber 42 rises and is higher than the pressure in the suction chamber 40, the valve member 72 is pressed against the valve seat 74, so that the bypass valve 70 closes and the pressure chamber 42 is separated from the suction chamber 40.
  • a filter 82 which is designed as a prefilter and through which the fuel drawn in by the gear pump from the storage tank flows, is connected upstream of the gear pump in the fuel line.
  • the gear pump is also followed by a further filter 83 in the fuel line, which is designed as a fine filter and through which the fuel required by the gear pump flows to the high-pressure fuel pump or to the fuel injection pump. It can also be provided that only the pre-filter 82 upstream of the gear pump is present and no fine filter.
  • a further housing part 84 is arranged on the gear pump, for example on the side of the housing part 10 facing away from the cover part 12, which has a recess facing the housing part 10, in which a pressure chamber 85 is formed.
  • the pressure chamber 85 is connected to a region downstream of the fine filter 83 so that the pressure in the pressure chamber 85 is the same as that downstream of the fine filter 83. If only the pre-filter 82 is present, the pressure chamber 85 is of a region downstream of the pre-filter 82 connected, so that the same pressure prevails in the pressure chamber 85 as downstream after the pre-filter 82 and before the gear pump.
  • the pressure chamber 85 is delimited in the recess of the housing part 84 on its side facing away from the housing part 10 by a movable wall 86 which is designed, for example, as a membrane.
  • the membrane 86 is by means of a
  • a rod 88 is supported, which projects through a bore in the housing part 10 and bears on the valve piston 60.
  • a prestressed spring 89 is arranged, which is designed, for example, as a helical compression spring. The membrane 86 is thus acted upon on the one hand by the pressure prevailing in the pressure chamber 85 and on the other hand by the prestressed spring 89.
  • the membrane 86 and with it the rod 88 by the spring 89 become a valve piston 60 printed out, whereby a further force acts in the closing direction on the valve piston 60 in addition to the compression spring 62. If the pressure in the pressure chamber 85 is high, the membrane 86 and with it the rod 88 are pulled away from the valve piston 60 against the force of the spring 89, so that a smaller force acts in the closing direction on the valve piston 60. If the fine filter 83 or the prefilter 82 are slightly contaminated, the result is the
  • liquid pump can alternatively also be designed, for example, as an internal gear pump or as a flight egg pump, the
  • Pressure limiting valve 50 for pressure control and the pressure chamber 85 for regulating the quantity can be used in the same way as described above.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

La présente invention concerne une pompe à liquides comprenant un boîtier (10,12) dans lequel est formée un chambre de pompe (14) dans laquelle se trouve au moins un élément d'acheminement (16,18) entraîné en rotation qui achemine du liquide d'une chambre d'aspiration (40) reliée à un réservoir, à une chambre de pression (42). La pompe à liquides présente une soupape de limitation de pression (50) qui sert à limiter la pression qui règne dans la chambre de pression (42) et qui présente un piston de soupape (60) disposé à l'intérieur du boîtier (10,12), ledit piston étant soumis à l'action d'un ressort de fermeture (62) précontraint qui le déplace dans la direction de fermeture, et à l'action de la pression qui règne dans la chambre de pression (42) qui le déplace dans la direction d'ouverture, et ledit piston libérant un canal de liaison (52) entre la chambre de pression (42) et la chambre d'aspiration (40), lors du dépassement d'une pression prédéterminée dans la chambre de pression (42). Un filtre (82) est disposé en amont de la pompe à liquides et/ou un autre filtre (83) est disposé en aval de la pompe à liquides, et ladite pompe à liquides comprend une chambre de pression (85) qui présente une liaison avec la zone située, dans le sens de circulation, en aval du filtre amont (82) ou une liaison avec la zone située, dans le sens de circulation, en aval du filtre aval (83). Grâce à la pression qui règne dans la chambre de pression (85), la force qui agit sur le piston de soupape (60) pour le déplacer dans la direction de fermeture, est modifiée de sorte que, lorsque la pression diminue dans la chambre de pression (85), la force qui agit sur le piston de soupape (60) pour le déplacer dans la direction de fermeture, augmente.
EP04762564A 2003-08-18 2004-07-30 Pompe a liquides Expired - Fee Related EP1658438B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10337849A DE10337849A1 (de) 2003-08-18 2003-08-18 Flüssigkeitspumpe
PCT/DE2004/001719 WO2005017361A1 (fr) 2003-08-18 2004-07-30 Pompe a liquides

Publications (2)

Publication Number Publication Date
EP1658438A1 true EP1658438A1 (fr) 2006-05-24
EP1658438B1 EP1658438B1 (fr) 2008-04-23

Family

ID=34177666

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762564A Expired - Fee Related EP1658438B1 (fr) 2003-08-18 2004-07-30 Pompe a liquides

Country Status (5)

Country Link
US (1) US20060228230A1 (fr)
EP (1) EP1658438B1 (fr)
JP (1) JP4164094B2 (fr)
DE (2) DE10337849A1 (fr)
WO (1) WO2005017361A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10968899B2 (en) 2015-11-20 2021-04-06 Positec Power Tools (Suzhou) Co., Ltd. Pump unit and handheld high pressure washer

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7640919B1 (en) * 2008-01-31 2010-01-05 Perkins Engines Company Limited Fuel system for protecting a fuel filter
ITBO20090386A1 (it) * 2009-06-15 2010-12-16 Cnh Italia Spa Pompa a cilindrata fissa
WO2020047804A1 (fr) * 2018-09-06 2020-03-12 苏州宝时得电动工具有限公司 Nettoyeur portatif à haute pression

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2636440A (en) * 1949-07-25 1953-04-28 Waukesha Foundry Co Sanitary pump with infinitely variable output
GB750673A (en) * 1953-06-26 1956-06-20 Zenith Carburateur Soc Du Improvements in or relating to gear pumps and applications thereof
GB1168489A (en) * 1966-12-09 1969-10-29 Frederick Arthur Driver Fuel Supply Systems of Fuel-Injection Pumps of Internal Combustion Engines and of Oil Burners
US4740140A (en) * 1985-12-11 1988-04-26 Sundstrand Corporation Pump having integral switch and bypass valve
DE4224973C2 (de) * 1992-07-29 1995-08-03 Glyco Metall Werke Fluidversorgungssystem mit Druckbegrenzung
DE19625564C2 (de) * 1996-06-26 2000-06-08 Bosch Gmbh Robert Kraftstoff-Förderpumpe für eine Kraftstoff-Einspritzpumpe für Brennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005017361A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10968899B2 (en) 2015-11-20 2021-04-06 Positec Power Tools (Suzhou) Co., Ltd. Pump unit and handheld high pressure washer
USRE49589E1 (en) 2015-11-20 2023-07-25 Positec Power Tools (Suzhou) Co., Ltd Pump unit and handheld high pressure washer

Also Published As

Publication number Publication date
WO2005017361A1 (fr) 2005-02-24
JP4164094B2 (ja) 2008-10-08
DE502004006939D1 (de) 2008-06-05
US20060228230A1 (en) 2006-10-12
EP1658438B1 (fr) 2008-04-23
DE10337849A1 (de) 2005-03-17
JP2006515042A (ja) 2006-05-18

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