CN103688056A - Gear pump and method for operating a gear pump - Google Patents

Gear pump and method for operating a gear pump Download PDF

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Publication number
CN103688056A
CN103688056A CN201280036019.0A CN201280036019A CN103688056A CN 103688056 A CN103688056 A CN 103688056A CN 201280036019 A CN201280036019 A CN 201280036019A CN 103688056 A CN103688056 A CN 103688056A
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CN
China
Prior art keywords
gear
pressure
gear pump
pump
fluid
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Granted
Application number
CN201280036019.0A
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Chinese (zh)
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CN103688056B (en
Inventor
A·富克斯
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F02M37/06—Feeding by means of driven pumps mechanically driven
    • 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
    • F02M59/447—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 means specially adapted to limit fuel delivery or to supply excess of fuel temporarily, e.g. for starting of the engine
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/38—Controlling fuel injection of the high pressure type
    • F02D41/3809—Common rail control systems
    • F02D41/3836—Controlling the fuel pressure
    • F02D41/3845—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped
    • F02D41/3854—Controlling the fuel pressure by controlling the flow into the common rail, e.g. the amount of fuel pumped with elements in the low pressure part, e.g. low pressure pump
    • 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
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • 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
    • F04C14/28—Safety arrangements; Monitoring
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/203—Fuel

Abstract

A gear pump for delivering a fluid, which gear pump has a rotatably mounted toothed wheel with external toothing and has a toothed ring with internal toothing, wherein a multiplicity of delivery chambers are formed by the meshing of teeth, and having a suction-side inflow duct and a pressure-side outflow duct, wherein between the inflow duct and the outflow duct there is formed a sealing region, wherein an orifice is formed in the sealing region on the side on which the delivery chambers decrease in size during the rotation of the toothed wheel and of the toothed ring.; A method for delivering a fluid in a high-pressure injection system, wherein a first hydraulic path is provided which leads from a pressure-side outflow duct of the gear pump via a high-pressure pump to a high-pressure accumulator, and a second hydraulic path is provided which leads from a pressure-side opening of the gear pump via a suction valve and a pump cylinder of the high-pressure pump to the high-pressure accumulator, wherein, in a standard operating mode in which the gear pump performs the function of predelivery of the fluid to the high-pressure pump, the fluid is supplied to the high-pressure accumulator via the first hydraulic path and the second hydraulic path, and wherein, in a starting mode for the rapid build-up of a high pressure in the high-pressure accumulator, the fluid is supplied to the high-pressure accumulator only via the second hydraulic path,; wherein at the same time the fluid quantity emerging from the gear pump via the first hydraulic path is supplied back to the inflow duct of the gear pump via a bypass path.

Description

Gear pump and for operating the method for gear pump
Technical field
The present invention relates to according to the gear pump of the preamble of claim 1 and according to the preamble of claim 10 for operating the method for gear pump.
Background technique
Gear pump, so-called Gerotor pump (Gerotorpumpen), is used for carrying fluid, for example, fuel is transported in the fuel injection system of an internal-combustion engine.
In normal pressure pump, supporting prejudicially with the gear ring of internal tooth and with the gear of external tooth.Here the inlet flow of fluid to be conveyed and discharge currents occur by fluid passage or by so-called input waist and discharge waist, and these fluid passages in the prior art throw of eccentric of relative bearing position are substantially symmetrically arranged.
For example in DE10035900A1, described one for fuel being transported to the internal gear pump of internal-combustion engine.The described internal gear pump in there has a gear ring with internal tooth and small gear with external tooth or gear, and this gear cooperatively interacts to produce pumping function with the gear ring with internal tooth.
In DE102006007554A1, described a kind of transfer pump, this transfer pump is combined in a motor.This transfer pump comprises first gear and second gear.Between two gears, form a conveying chamber.The second gear Yong Qi center is bearing in an axle.The first gear is an external gear and forms rotor, and the second gear is an internal gear, and it is driven in the eccentric central position of the first gear.
The essential high pressure of setting up in short-term when engine starting, especially when one of expectation is started fast.
Fuel supply system and the method for cranking internal combustion engine of an internal-combustion engine have been described in DE102007058231A1, by the method basis, for dragging beginning and the minimum time in the time lag between the release of the first course of injection of motor, determine a pressure minimum, i.e. the required pressure of the first course of injection when engine start.
Yet the starting method of this known internal-combustion engine for a common rail system has its shortcoming, quick starting only just can realize by expensive configuration and/or control.Quick starting is especially vital for the diesel engine with shutdown robot device (start and stop of Idle Start Stop " ISS " idling).
Therefore be worth expectation, when starting with simple and cost on the high pressure realized in short-term of favourable mode set up.
Summary of the invention
According to the present invention proposes one for delivery of the gear pump of fluid, it has the gear with external tooth and the gear ring with internal tooth of a rotatably support, this gear and gear ring be supporting prejudicially mutually, common form tooth coupling and in order to produce the ingear cooperation of conveying function, wherein by tooth, be coupled and form a plurality of conveying chambers, and one of them suction side input channel is disposed in the first angular regions, in this first angular regions, when gear and gear ring rotation, conveying chamber increases, and one on the pressure side discharge route be disposed in the second angular regions, in this second angular regions, when gear and gear ring rotation, conveying chamber dwindles, wherein between input channel and discharge route, form a sealing area, wherein in sealing area, in the side that conveying chamber dwindles when when gear and gear ring rotation, structure has a hole.
By configuration according to the present invention, can provide in short-term by the electric gear wheel pump of the function of tonic chord favourable, that there is transfer the fuel on cost the roughly high pressure of 120 bar.This hole is arranged in the second angular regions that conveying chamber dwindles when gear pump is worked, and in this region, when gear ring and gear rotate, has set up a very high squeeze pressure at fluid to be conveyed, as diesel fuel.This high squeeze pressure will be utilized by configuration according to the present invention, and its mode is that fluid to be conveyed is not to flow to high-pressure service pump by discharge route when starting, but the additional holes in the second angular regions of gear pump is exported when engine starting.
According to this hole of preferred form of implementation, play the effect in squeeze pressure unloading hole.Particularly preferably be, this hole is only made in the extreme littlely in the case, can advantageously support providing of high pressure in short-term thus.
According to the arc length separately of another preferred form of implementation input channel and discharge route, be less than 180 °.
According to another preferred form of implementation sealing area, there is first portion region, in this region division side that conveying chamber increases when when gear and gear ring rotation.
According to another preferred form of implementation sealing area, there is second portion region, in this region division side that conveying chamber dwindles when when gear and gear ring rotation.
Preferably this hole is arranged on the centre in the second portion region of sealing area substantially.
In addition preferably, in the second angular regions conveying chamber footpath upwards by between gear and gear ring through the tooth coupling of a line contact segment and sealed.
According to another this gear pump of preferred form of implementation, be an internal gear pump, wherein with the gear ring of internal tooth, play the effect of rotor.
Preferably this gear pump is installed on a high-pressure service pump.
In addition according to the present invention, propose one for operating a gear pump to transport fluid into a high-pressure injection system, especially the method in a common rail system, wherein be provided with first hydraulic path, this first hydraulic path by one of gear pump on the pressure side discharge route by a high-pressure service pump, import a high-pressure storage, and be provided with second hydraulic path, by one of gear pump squeeze pressure unloading hole on the pressure side, a pumping cylinder by a suction valve and high-pressure service pump imports high-pressure storage to this second hydraulic path, wherein at gear pump, carry out in the normal operating mode of the function of carrying fluid to high-pressure service pump, fluid is fed to high-pressure storage by the first hydraulic path and the second hydraulic path, and wherein in an originate mode, in order to set up in short-term a high-pressure liquid at high-pressure storage, only by the second hydraulic path, be fed to high-pressure storage, the Fluid Volume of wherein side by side being discharged by the first hydraulic path by gear pump is input to again the input channel of gear pump by a bypass path.By the method according to this invention, in order to start, can with simple methods, to high-pressure service pump input, load by electric gear wheel pump favourable on cost the fuel of high pressure.
Accompanying drawing explanation
Hereinafter with reference to accompanying drawing, embodiments of the invention are at length described.Accompanying drawing represents:
Fig. 1: according to the cross section of prior art electric gear wheel pump;
Fig. 2: shown in Fig. 1 according to the summary view of the input channel of electric gear wheel pump of prior art and the layout of discharge route;
Fig. 3: according to the summary view of the layout of the input channel of a form of implementation and discharge route; And
Fig. 4: according to the hydraulic scheme of the high-pressure injection system of a form of implementation.
Concrete form of implementation
Fig. 1 represents according to the summary view of prior art electric gear wheel pump 1.This gear pump 1 comprises a gear mesh, this gear mesh by one play rotor effect, with gear ring 2 and gear 3 or the small gear with external tooth of internal tooth, form.With the open of external tooth, relatively with the gear 2 of internal tooth is eccentric, arranges and turn on a vertical journal 4 rotationally.If be driven into and rotatablely move with the gear 3 of external tooth, with the external tooth of the gear 3 of external tooth, be engaged in the internal tooth of gear ring 2 and produce the conveying stream of a fluid, in tooth turn of tidal stream body, move.Play the sense of rotation of the gear ring 2 with internal tooth of rotor effect by representing with the arrow of label 5 indication, be here counterclockwise.With the gear ring 2 of internal tooth and with the gear 3 of external tooth, supported slidably and there is a corresponding bearing play.Between this external gear ring 2 and gear 3, form a plurality of conveying chambers 10.
In addition by the gear ring 2 with internal tooth and with the gear mesh that the gear 3 of external tooth forms, be arranged in a housing (not shown).With the gear ring 2 of internal tooth and with gear 3 supporting prejudicially mutually as described above of external tooth, wherein the degree of eccentricity represents by label 6 in addition.
Electric gear wheel pump 1 also has one for making suction side input channel 7 and the on the pressure side discharge route 8 for fluid to be conveyed is derived by gear pump 1 of the inside of fluid importing gear pump 1, as shown in by a dotted line.Here input channel 7 and output channel 8 are mutually arranged and are formed input waist or discharge waist (see figure 2) in 180 ° of ground of skew.Input channel 7 and discharge route 8 are formed in the lid of unshowned housing here or gear pump 1, and their length is slightly less than in the angle of 180 ° because the inner sealing between suction side and compressed side respectively extends in one.Input channel 7 is arranged in the first angular regions 9 in the case, and in this angular regions, when gear ring 2 and gear 3 rotation, conveying chamber 10 increases towards anticlockwise sense of rotation 5.And discharge route 8 is arranged in the second angular regions 11, in this angular regions, when gear ring 2 and gear 3 rotation, conveying chamber 10 dwindles towards sense of rotation 5.
Fig. 2 be shown in Fig. 1 according to the summary view of the layout of the input channel 7 of the electric gear wheel pump 1 of prior art and discharge route 8.Input channel 7 and discharge route 8 are respectively configured input waist and discharge waist and respectively have the length being less than in the angular regions of 180 °, so that in the suction side of electric gear wheel pump 1 and on the pressure side or between input channel 7 and discharge route 8, have formed a sealing area 12.Here sealing area 12 comprises corresponding to the first angle [alpha] 1 first portion region 19, this region division in this side, this side be taken in gear 3 and gear ring 2 while rotating conveying chamber 10 increase; And comprise corresponding to the second angle [alpha] 2 second portion region 20, this region division in that side, this side be taken in gear 3 and gear ring 2 while rotating conveying chamber 10 dwindle.
Fig. 3 is according to the summary view of the layout of the input channel 7 of a form of implementation and discharge route 8.As appreciable by this figure, with the form of implementation shown in Fig. 2 differently with the second angle [alpha] 2accordingly, in the second portion region 20 of sealing area 12, roughly in part area, 20 centre is provided with an additional holes 13.Sealing area 12 between input channel 7 and discharge route 8 extend in the second angle [alpha] 2on, therefore and be arranged in the region in the side that conveying chamber 10 dwindles when gear ring 2 and gear 3 rotate on by 5 indicated directions, a conveying chamber 10(who moves on this region is shown in Fig. 1) sealing completely on certain rotation angle.Because the conveying chamber 10 in this region dwindles when rotating and at the second portion region of sealing area 12 20(α 2) central diameter is upwards sealed by being coupled through the tooth of a line contact segment between gear ring 2 and gear 3, wherein axial bearing play (rotor is to housing and lid) can be selected very littlely, when rotating, here forms during especially at high rotating speed very high " squeeze pressure ".By this, be roughly arranged on second portion region 20(α 2) in the middle of this additional holes of additional holes 13 – as much as possible little and play what is called and go the Zuo Yong – in nip load hole can make to be extruded dielectric leakage out, to for example flow to a high-pressure storage 18(when starting in short-term, see Fig. 4).
In Fig. 4, represent according to the hydraulic scheme of the high-pressure injection system 14 of a form of implementation.As shown here, the fuel 16, for example diesel oil that are arranged in a fuel tank 15 are carried and are input to a high-pressure storage 18 by a high-pressure service pump 17 by an electric gear wheel pump 1, as also will explained in detail below.In the mode of operation of a standard, after engine starting, the fuel carried by gear pump 1 here 16 had not only been input to high-pressure storage 18 by the first path Q1 but also by the second path Q2.Even the quantity delivered that is input to high-pressure storage 18 by the second path Q2 in the case than the quantity delivered by the first path Q1 input little and when high rotating speed, also increase not obvious, appreciable as the plotted curve of the lower-left side by this figure.
17 pairs of high-pressure service pumps transport when normal operating mode fuel load high pressure and and then flow to high-pressure storage 18, by there fuel, by unshowned injection valve, be ejected in the firing chamber of internal-combustion engine.
Yet be arranged in electric gear wheel pump 1 on high-pressure service pump 17 hydraulic pipe line shown here and can with high pressure (～120 bar), provide certain fuel quantity in short-term when engine starting.In a kind of working condition " ISS " (Idle Start Stop), – should set up the roughly starting pressure of 120 bar by electric gear wheel pump 1 in this working condition in the case, the high pressure pumping cylinder 20 that is only the second fuel path Q2 by a suction valve 19 and high-pressure service pump 17 is connected to high-pressure storage 18, to set up in short-term there required pressure when engine starting.In order to reach required starting pressure, here utilize in conjunction with the configuration described in Fig. 3, the fuel under high pressure wherein forming with the methods described above in the conveying chamber 10 in the second angular regions 11 is by by being arranged in sealing area 12(α 2) the additional hole 13 in second portion region 20 leak out and be input to high-pressure storage 18 by the second path Q2.Low for the total torque demand of electric gear wheel pump 1 is remained, need to be in this mode of operation " ISS " high-pressure service pump 17 standard quantity delivered by the delivery pathways of being indicated by Q1 in normal operating mode be fed back to suction side by a bypass path 21.
In the time of can working as engine starting with electric gear wheel pump 1 favourable on a cost by configuration according to the present invention, produce in short-term a high pressure, this high pressure is particularly useful for a common rail system.

Claims (10)

1. for delivery of the gear pump (1) of fluid, gear with external tooth (3) and the gear ring with internal tooth (2) with a rotatably support, this gear and gear ring be supporting prejudicially mutually, common form tooth coupling and in order to produce the ingear cooperation of conveying function, wherein by tooth, be coupled and form a plurality of conveying chambers (10), and one of them suction side input channel (7) is disposed in the first angular regions (9), in this first angular regions, when gear (3) and gear ring (2) rotation, conveying chamber (10) increases, and one on the pressure side discharge route (8) be disposed in the second angular regions (11), in this second angular regions, when gear (3) and gear ring (2) rotation, conveying chamber (10) dwindles, wherein between input channel (7) and discharge route (8), form a sealing area (12), it is characterized in that: in sealing area (12), in the side that conveying chamber (10) dwindles when when gear (3) and gear ring (2) rotation, structure has a hole (13).
2. according to the gear pump of claim 1 (1), it is characterized in that: the effect in squeeze pressure unloading hole is played in this hole.
3. according to the gear pump of claim 1 or 2 (1), it is characterized in that: the arc length separately of input channel (7) and discharge route (8) extends in one and is less than in the angular regions of 180 °.
4. according to any one in claims 1 to 3 or multinomial gear pump (1), it is characterized in that: sealing area (12) has and extends in the first angle (α 1) on first portion region (19), this angle is arranged in the side that conveying chamber (10) increases when gear (3) and gear ring (2) rotate.
5. according to any one in claim 1 to 4 or multinomial gear pump (1), it is characterized in that: sealing area (12) has and extends in the second angle (α 2) on second portion region (20), this angle is arranged in the side that conveying chamber (10) dwindles when gear (3) and gear ring (2) rotate.
6. according to the gear pump of claim 5 (1), it is characterized in that: hole (13) are arranged on the centre in the second portion region (20) of sealing area (12) substantially.
7. according to any one in claim 1 to 6 or multinomial gear pump (1), it is characterized in that: in the second angular regions (11), line contact segment is upwards passed through by the tooth coupling between gear (3) and gear ring (2) and sealed in conveying chamber (10) footpath.
8. according to any one in claim 1 to 7 or multinomial gear pump (1), it is characterized in that: this gear pump (1) is an internal gear pump, and wherein gear ring (2) plays the effect of rotor.
9. according to any one in claim 1 to 8 or multinomial gear pump (1), it is characterized in that: this gear pump (1) can be installed on a high-pressure service pump.
For operate one especially according to the gear pump of claim 1 (1) to transport fluid into a high-pressure injection system (14), the method in a common rail system especially, it is characterized in that: be provided with a first hydraulic path (Q 1), this first hydraulic path by one of gear pump (1) on the pressure side discharge route (8) by a high-pressure service pump (17), lead to high-pressure storage (18), and be provided with a second hydraulic path (Q 2), by the pressure side opening (13) of gear pump (1), the pumping cylinder (20) by a suction valve (19) and high-pressure service pump leads to high-pressure storage (18) to this second hydraulic path, wherein, at gear pump (1), carry out in the normal operating mode of the function of carrying in advance fluid to high-pressure service pump (14), fluid is by the first hydraulic path (Q 1) and the second hydraulic path (Q 2) be fed to high-pressure storage (18), and wherein in an originate mode (ISS) in order to set up in short-term a high pressure at high-pressure storage (18), fluid is only by the second hydraulic path (Q 2) be fed to high-pressure storage (18), wherein side by side by gear pump (1), pass through the first hydraulic path (Q 1) Fluid Volume of discharging is input to again the input channel (7) of gear pump (1) by a bypass path (21).
CN201280036019.0A 2011-07-22 2012-06-12 Gear pump and the method being used for operating gear pump Expired - Fee Related CN103688056B (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE201110079671 DE102011079671A1 (en) 2011-07-22 2011-07-22 Gear pump and method for operating a gear pump
DE102011079671.1 2011-07-22
PCT/EP2012/061126 WO2013013879A2 (en) 2011-07-22 2012-06-12 Gear pump and method for operating a gear pump

Publications (2)

Publication Number Publication Date
CN103688056A true CN103688056A (en) 2014-03-26
CN103688056B CN103688056B (en) 2016-08-24

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CN201280036019.0A Expired - Fee Related CN103688056B (en) 2011-07-22 2012-06-12 Gear pump and the method being used for operating gear pump

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EP (1) EP2734733B1 (en)
JP (1) JP5759628B2 (en)
KR (1) KR20140040242A (en)
CN (1) CN103688056B (en)
BR (1) BR112014001366A2 (en)
DE (1) DE102011079671A1 (en)
WO (1) WO2013013879A2 (en)

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Publication number Priority date Publication date Assignee Title
DE2720406A1 (en) * 1977-05-06 1978-11-09 Audi Nsu Auto Union Ag INTERNAL GEAR PUMP PRESENTLY FOR COMBUSTION ENGINES IN DRIVE UNITS OF MOTOR VEHICLES
DE4303328A1 (en) * 1993-02-05 1994-08-11 Vdo Schindling Gerotor for delivering fluid, especially as a fuel delivery unit for motor vehicles
JPH09126153A (en) * 1995-10-30 1997-05-13 Aisin Seiki Co Ltd Oil pump device
CN1414246A (en) * 2001-10-25 2003-04-30 京三电机株式会社 Electric fuel pump for vehicle
CN1875189A (en) * 2003-10-29 2006-12-06 Gkn金属烧结有限公司 Double or multiple pump

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JPH0914152A (en) * 1995-06-30 1997-01-14 Jatco Corp Internal gear type rotary pump
US6102684A (en) * 1998-09-14 2000-08-15 Walbro Corporation Cavitation noise abatement in a positive displacement fuel pump
DE10035900A1 (en) 2000-07-21 2002-01-31 Bosch Gmbh Robert Internal gear pump
DE102006007554A1 (en) 2006-02-16 2007-08-23 Hydraulik-Ring Gmbh Feed pump for a urea solution, to treat heavy vehicle motor exhaust gases, is an electromotor with an integrated gear pump of two meshing cogwheels rotated by a magnetic field
DE102007058231A1 (en) 2007-12-04 2009-06-10 Robert Bosch Gmbh Internal-combustion engine i.e. petrol internal-combustion engine, starting method for motor vehicle, involves controlling engine such that time interval from beginning of driving of engine is similar with operating parameters of engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2720406A1 (en) * 1977-05-06 1978-11-09 Audi Nsu Auto Union Ag INTERNAL GEAR PUMP PRESENTLY FOR COMBUSTION ENGINES IN DRIVE UNITS OF MOTOR VEHICLES
DE4303328A1 (en) * 1993-02-05 1994-08-11 Vdo Schindling Gerotor for delivering fluid, especially as a fuel delivery unit for motor vehicles
JPH09126153A (en) * 1995-10-30 1997-05-13 Aisin Seiki Co Ltd Oil pump device
CN1414246A (en) * 2001-10-25 2003-04-30 京三电机株式会社 Electric fuel pump for vehicle
CN1875189A (en) * 2003-10-29 2006-12-06 Gkn金属烧结有限公司 Double or multiple pump

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CN103688056B (en) 2016-08-24
KR20140040242A (en) 2014-04-02
WO2013013879A2 (en) 2013-01-31
JP2014521014A (en) 2014-08-25
BR112014001366A2 (en) 2017-02-21
WO2013013879A3 (en) 2013-08-22
DE102011079671A1 (en) 2013-01-24
EP2734733B1 (en) 2018-08-08
JP5759628B2 (en) 2015-08-05
EP2734733A2 (en) 2014-05-28

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