WO2011069713A2 - Pompe à engrenages extérieurs - Google Patents

Pompe à engrenages extérieurs Download PDF

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Publication number
WO2011069713A2
WO2011069713A2 PCT/EP2010/065181 EP2010065181W WO2011069713A2 WO 2011069713 A2 WO2011069713 A2 WO 2011069713A2 EP 2010065181 W EP2010065181 W EP 2010065181W WO 2011069713 A2 WO2011069713 A2 WO 2011069713A2
Authority
WO
WIPO (PCT)
Prior art keywords
housing
gear pump
external gear
pressure
housing ring
Prior art date
Application number
PCT/EP2010/065181
Other languages
German (de)
English (en)
Other versions
WO2011069713A3 (fr
Inventor
Siamend Flo
Heinz Siegel
Juergen Arnold
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
Priority to EP10765426A priority Critical patent/EP2510239A2/fr
Priority to CN201080055661.4A priority patent/CN102648350B/zh
Publication of WO2011069713A2 publication Critical patent/WO2011069713A2/fr
Publication of WO2011069713A3 publication Critical patent/WO2011069713A3/fr

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
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—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
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/70—Use of multiplicity of similar components; Modular construction
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/04—Force
    • F04C2270/044—Force axial

Definitions

  • the invention relates to an external gear pump according to the preamble of claim 1.
  • an external gear pump which has two rotatable, meshing gears.
  • the gears are mounted in a housing.
  • a fluid is sucked in on a suction side, pressurized and fed to a pressure side.
  • the object of the present invention is to provide an external gear pump which has sufficiently large flow cross sections even on a large flow, especially on the suction side, so that vapor bubbles do not form or only to a small extent at all operating points.
  • the external gear pump according to the invention should be particularly easy to manufacture and durable.
  • the housing ring Due to the inventive design of the housing ring, it is possible to hydraulically connect the suction and the low pressure channel with a first approximate twice as large cross-section. This significantly reduces the pressure loss on the suction side of the external gear pump. As a result, no cavitation occurs even with external gear pumps with very wide gears and correspondingly high flow rate.
  • Breakthrough and at least one channel are arranged in the housing ring and this housing ring must be as thick as the tooth width of the gears, it is readily possible to provide this housing ring always with the apertures and channels according to the invention in the housing ring when the flow rate is especially big. Then namely the tooth width of the gears and the thickness of the housing ring are also large. Therefore, then in the housing ring is always enough material to the
  • the additional flow cross section according to the invention by an opening which connects the two end faces of the housing ring together and recessed at the end faces channels which connect the openings with the suction region and the pressure range of the external gear pump made.
  • This shape is particularly advantageous because it has a symmetrical structure, which is in terms of
  • this shape is also very suitable for production by sintering, since the aperture and the channels can be produced easily with a two-part sintering tool. Also, the manufacturing costs are kept low.
  • a web is provided between the two channels running on the end faces of the housing ring.
  • Housing ring are welded together on the outer circumference.
  • the three components mentioned are fixed relative to each other.
  • This type of fixation is particularly well suited for mass production because it is easy to automate and is very reliable to operate. So that the weld does not protrude radially outward beyond the outer diameter of the housing parts or of the housing ring, a chamfer is provided on the housing parts and / or the housing ring. The weld is laid in this chamfer.
  • weld spatter does not adhere to the cylindrical outer surface of the housing ring and housing parts, which would adversely affect the manufacture and assembly of the welded components in the outer housing of the gear pump according to the invention.
  • the invention further relates to a fuel injection system with an external gear pump described above.
  • Their embodiments and advantages have already been explained above. These explanations are hereby incorporated by reference.
  • Figure 1 is a schematic view of a fuel injection system with an internal combustion engine and with an external gear pump for the delivery of fuel;
  • FIG. 2 shows a view of the external gear pump according to FIG. 1 along a section line designated II-II in FIG. 3;
  • FIG. 3 shows a view of the external gear pump according to FIG. 1 along a section line designated III-III in FIG.
  • Figure 4 is an enlarged view of the gear arrangement of
  • FIG. 5 shows a longitudinal section through the housing ring 72 along a section line designated IV-IV in FIG.
  • a fuel injection system designated overall by the reference numeral 10 in FIG. 1 for supplying an internal combustion engine 12 with fuel comprises an external gear pump 14.
  • the fuel injection system 10 has a reservoir 16 for storing fuel.
  • a prefeed pump 18 which preferably by means of a controllable drive device, in particular in the form of a
  • Electric motor 20 is driven, fuel is conveyed from the reservoir 16 in a low-pressure line 22.
  • the flow rate of the fuel injection system 10 can be adjusted so that delivery losses can be reduced, which results by promoting an excess amount of fuel, which then has to be returned to the reservoir 16.
  • To limit the fuel pressure in the low pressure line 22 is a
  • Low-pressure limiting valve 24 is provided, by means of which at
  • the low pressure line 22 opens at an input 26 of the
  • External gear pump 14 This acts on the supplied via the input 26 fuel at high pressure.
  • the pressurized fuel passes through an output 28 of the external gear pump 14 to a
  • High-pressure line 30 which leads to a fuel collecting device in the form of a rail 32.
  • the rail 32 supplies injectors 34 with pressurized fuel.
  • the injection valves 34 are each one of the combustion chambers of
  • the pressure in the rail 32 is detected by means of a pressure sensor 36.
  • a voltage signal corresponding to the detected pressure can be detected by means of a
  • Data line 38 are supplied to a control unit 40.
  • the control unit 40 is coupled to the electric motor 20 by means of a control line 42.
  • the internal combustion engine 12 comprises sections shown
  • Internal combustion engine housing 44 for example in the form of a cylinder head.
  • the engine housing 44 has an outwardly facing
  • the internal combustion engine 12 includes a
  • Shaft in particular in the form of a camshaft which is rotatably mounted about a shaft axis 50 on the engine housing 44 and forms a drive shaft 48 for the external gear pump 14.
  • the drive shaft 48 may be formed by a separate from a shaft of the internal combustion engine 12 shaft.
  • a housing opening 52nd In the engine housing 44 is a housing opening 52nd
  • Shaft end 54 extends beyond the housing surface 46 into the environment of the internal combustion engine 12.
  • the external gear pump 14 has a pot-shaped outer housing 56, which is connected in particular by means of a welded flange 58 to the engine housing 44, for example by means of a screw connection.
  • the outer housing 56 has a housing projection 60 which extends in the direction of the internal combustion engine 12 and which is inserted into the housing opening 52 of the internal combustion engine 12.
  • Housing projection 60 has a circular cross-section
  • Housing recess 62 which allows passage of the drive shaft 48.
  • a plurality of housing parts are arranged, namely a first housing part 66, a second housing part 68 spaced therefrom and a third housing part 70 acting as a housing cover.
  • the third housing part 70 is welded to the outer housing 56. It is preferred if the
  • housing parts 66, 68 and 70 mutually parallel planar surfaces, so that the housing parts form metallic sealing surfaces with these flat surfaces.
  • a sealing force can be generated, which pushes the housing parts 66 and 68 into the outer housing 56.
  • Housing part 68 is a housing ring 72 is arranged, in which a
  • Gear arrangement 74 is arranged.
  • the gear arrangement 74 forms the actual conveying unit of the external gear pump 14.
  • the gear arrangement 74 is mounted in the axial direction between the first housing part 66 and the second housing part 68.
  • the housing ring 72 serves for the radial mounting of the
  • welds 168 In order to position the housing parts 66 and 68 and the housing ring 72 relative to one another, these are welded together by welds 168 (see FIG. 2).
  • the welds 168 need not be liquid-tight; she can also be interrupted.
  • the welds 168 are divided into two angular segments of about 100 °.
  • the weld 168 is preferably provided where the housing ring 72 has a large material thickness. So that the welds 168 do not protrude in the radial direction beyond the housing parts 66 and 68 and the housing ring 72, a chamfer is on these components
  • the external gear pump 14 has a low-pressure side connected to the input 26 low-pressure channel 76, which is formed in the third housing part 70.
  • the low-pressure channel 76 opens at a suction kidney 78 (see FIG. 1), which is formed in the second housing part 68.
  • Housing part 66 has one of the shape of the suction kidney 78 corresponding
  • the external gear pump 14 On the pressure side, the external gear pump 14 has a high-pressure channel 82 connected to the outlet 28, which is formed in the third housing part 70.
  • the high-pressure passage 82 is connected to a pressure kidney 84, which is formed in the second housing part 68.
  • a counter kidney 86 In the first housing part 66 is a counter kidney 86 corresponding to the shape of the pressure kidney 84
  • Gear assembly 74 is charged evenly from both sides with pressure.
  • the external gear pump 14 includes a pressure relief valve 88 (see FIG. 2), by means of which a fluid connection between the high-pressure channel 82 and the low-pressure channel 76 can be produced when a predeterminable operating pressure is exceeded.
  • the pressure limiting valve 88 is arranged in a connecting channel 90 which extends between the high-pressure channel
  • the pressure limiting valve 88 has a valve seat 92 pressed into the connection channel 90, a valve body 94 cooperating with the valve seat 92 and a valve spring 96 which presses the valve body 94 against the valve seat 92.
  • Connecting channel 90 is formed in the form of a blind hole and closed at the open end by means of a pressed-in stopper 98.
  • the gear assembly 74 includes a first gear 100 that meshes with a second gear 102.
  • the first gear 100 has a smaller diameter than the second gear 102.
  • the first gear 100 is driven by the second gear 102 (see FIGS. 2 and 3).
  • the second gear 102 is about an axis of rotation associated with this gear
  • the axis of rotation 104 is at least approximately collinear with the shaft axis 50 of the drive shaft 48.
  • the second gear 102 has a central opening 106 into which the shaft end 54 of the drive shaft 48 is inserted.
  • the drive shaft 48 has a main portion 108 which extends within the
  • Internal combustion engine housing 44 extends.
  • the main section 108 is followed, in the direction of the external gear pump 14, by a shaft shoulder 110, a shaft-guiding surface 112 that is in particular convex-shaped, a shaft section 114, and a shaft journal 116 arranged on the front side.
  • the shaft shoulder 110 penetrates the housing recess 62 of the
  • a sealing device 118 is provided, which is designed in particular in the form of a radial sealing ring. This is arranged within the housing projection 60 and comprises a schematically illustrated first sealing lip 120, by means of which an ingress of oil from the
  • the sealing device 118 comprises a second
  • Sealing lip 122 by means of which a leakage of fuel from the interior of the external gear pump 14 out into the interior of the internal combustion engine 12 is prevented.
  • the shaft guide surface 112 is mounted in a cylindrical bearing surface 124, which is formed on the first housing part 66.
  • the bearing surface 124 is adjoined by a centering surface 126 inclined relative to the bearing surface 124, by means of which the insertion of the shaft guide surface 112 into the bearing surface 124 is facilitated.
  • the shaft section 114 has, for example, a polygonal profile, in particular a hexagonal profile. This profile works with a
  • the opening 106 is slightly larger than the profile of the Shaft portion 114, so that the second gear 102 is connected in the radial direction play with the drive shaft 48.
  • the drive shaft 48 and the external gear pump 14 are moved toward each other in one of the joining directions designated 128 and 130.
  • the joining directions 128 and 130 are collinear with the axis of rotation 104 of the second gear 102 and with the shaft axis 50 of the drive shaft 48.
  • the shaft journal 116 is preferably cylindrical and serves during the insertion of the shaft end 54 in the external gear pump 14 as a further insertion aid.
  • the external gear pump 14 is attached to the free shaft end 54. Damage to the sealing device 118 during the joining of the drive shaft 48 and the second gear 102 is prevented by the shaft journal 116 first engaging the central opening 106 of the second gear 102 before the shaft shoulder 110 is inserted into the housing recess 62 and into engagement with the shaft Sealing lips 120 and 122 is brought.
  • the first gear 100 is rotatable about a rotation axis 132.
  • the position of the axis of rotation 132 of the first gear 100 and the axis of rotation 104 of the second gear 102 relative to a plane of rotation of the gears is play-related.
  • the gears 100, 102 are supported by their meshing engagement in a Kämm Colour 134 and by contact with a respective one of the gears 100, 102 associated bearing surface.
  • the first gear 100 is mounted on a sectionally cylindrical jacket-shaped first bearing surface 136.
  • the first bearing surface 136 extends over an angular segment 138 of, for example, about 70 degrees to about 90 degrees
  • the first housing surface 136 merges into a first housing surface 140, which likewise has a cylinder-shaped jacket.
  • cylinder jacket-shaped second bearing surface 142 which extends over an angular segment 144 of, for example, about 30 degrees to about 50
  • the second bearing surface 142 merges into a second housing surface 146, likewise in the form of a cylinder jacket, in sections.
  • the bearing surfaces 136 and 142 and the housing surfaces 140 and 146 wrap around the gears 100, 102. Due to the fact that the gears 100, 102 have a significantly different diameter, the wrap angle of said surfaces is particularly large.
  • the bearing surfaces 136 and 142 and the combing region 134 define between them a suction region 148, by means of which the outer gear pump 14 is a medium to be conveyed fed.
  • the combing area 134 together with a transition between the housing surfaces 140 and 146, delimits a pressure region 150 of the external gear pump 14.
  • the external gear pump 14 comprises a first force-generating device 152, which is designed in particular in the form of a pressure chamber 154.
  • the pressure chamber 154 has a chamfer geometry, see also Figure 2.
  • Pressure chamber 154 extends around first gear 100 along with first housing surface 140.
  • the external gear pump 14 further includes a second one
  • Force generating device 156 in the form of a second pressure chamber 158. Also, this pressure chamber has a chamfer geometry and extends
  • Pressure chambers 154 and 158 each two times on both sides of the gears 100, 102 arranged so that the gears 100, 102 are loaded in the axial direction from both sides with the same pressure.
  • the gears 100, 102 each have a plurality of teeth 160.
  • the teeth 160 have radially outwardly facing tooth head surfaces, which are correspondingly curved in the curvature of an associated bearing surface 136, 142.
  • Input 26 supplied fluid to be delivered.
  • the second gear 102 is driven in a drive direction 164. In this way, a fluid to be delivered from the suction region 148 along the bearing surfaces 142 and 136 and along the housing surfaces 140 and 146 of the
  • Pressure chambers 154 and 158 is generated by means of the pressurized fluid to be conveyed a force which a gear 100, 102 against a This gear associated bearing surface 136, 142 presses.
  • the tooth head surfaces 162 of the toothed wheels 100, 102 facing radially outwards each come into sealing contact with an associated bearing surface 136, 142.
  • an opening 170, 174 is formed in each extension of the high-pressure channel 82 and / or the low-pressure channel 76 in the housing ring 72.
  • Flow cross-section increases both in the suction region 148 and in the pressure region 150 of the gear assembly 74, which has a positive effect on the performance and efficiency of the gear pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne une pompe à engrenages extérieurs (14) présentant deux roues dentées rotatives (100, 102) en engrènement mutuel. Selon l'invention, au moins une roue dentée (100) est montée en sens radial par rapport à son axe de rotation (132) par contact des têtes de dent (162) orientées radialement vers l'extérieur avec une surface d'appui (136) située radialement à l'extérieur. Le comportement en service et le rendement de la pompe à engrenages extérieurs (14) selon l'invention sont améliorés par un guidage optimisé du liquide à transporter aussi bien du côté aspiration que du côté refoulement grâce à des orifices (170, 174) et des conduits (172, 176).
PCT/EP2010/065181 2009-12-08 2010-10-11 Pompe à engrenages extérieurs WO2011069713A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP10765426A EP2510239A2 (fr) 2009-12-08 2010-10-11 Pompe à engrenages extérieurs
CN201080055661.4A CN102648350B (zh) 2009-12-08 2010-10-11 外啮合齿轮泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910047610 DE102009047610A1 (de) 2009-12-08 2009-12-08 Außenzahnradpumpe
DE102009047610.5 2009-12-08

Publications (2)

Publication Number Publication Date
WO2011069713A2 true WO2011069713A2 (fr) 2011-06-16
WO2011069713A3 WO2011069713A3 (fr) 2011-10-13

Family

ID=43554460

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/065181 WO2011069713A2 (fr) 2009-12-08 2010-10-11 Pompe à engrenages extérieurs

Country Status (4)

Country Link
EP (1) EP2510239A2 (fr)
CN (1) CN102648350B (fr)
DE (1) DE102009047610A1 (fr)
WO (1) WO2011069713A2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016224445A1 (de) 2016-12-08 2018-06-14 Robert Bosch Gmbh Zahnradpumpe
IT201700067438A1 (it) * 2017-06-16 2018-12-16 Gkn Sinter Metals Ag Disposizione di pompa.
FR3080892B1 (fr) * 2018-05-04 2020-04-03 Exoes Pompe a engrenages pour la circulation d’un fluide
EP3936725A4 (fr) * 2019-03-08 2022-03-23 Shimadzu Corporation Moteur ou pompe à engrenages hélicoïdaux

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006056843A1 (de) 2006-12-01 2008-06-05 Robert Bosch Gmbh Förderaggregat

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2440986A (en) * 1943-03-06 1948-05-04 Gen Motors Corp Pump
US3076413A (en) * 1959-12-29 1963-02-05 Parker Hannifin Corp High pressure aircraft gear pump
GB1113461A (en) * 1964-07-31 1968-05-15 Shimadzu Corp Hydraulic fluid gear pump or motor
BE1012051A6 (nl) * 1998-06-30 2000-04-04 Z F Getriebe N V Sint Truiden Tandwielpomp, alsmede variabele transmissie die met dergelijke tandwielpomp is uitgerust.
CA2514823C (fr) * 2002-06-03 2010-09-21 Kfi Engineering, Inc. Pompe a engrenage
JP2005337136A (ja) * 2004-05-27 2005-12-08 Toyota Motor Corp 外接ギヤポンプ
DE102007031901B4 (de) * 2007-07-09 2014-06-12 Schwäbische Hüttenwerke Automotive GmbH & Co. KG Umlaufverdrängerpumpe mit Füllgrad steigerndem Einlass
DE102008054751A1 (de) 2008-12-16 2010-06-17 Robert Bosch Gmbh Außenzahnradpumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006056843A1 (de) 2006-12-01 2008-06-05 Robert Bosch Gmbh Förderaggregat

Also Published As

Publication number Publication date
WO2011069713A3 (fr) 2011-10-13
EP2510239A2 (fr) 2012-10-17
CN102648350B (zh) 2015-08-19
CN102648350A (zh) 2012-08-22
DE102009047610A1 (de) 2011-06-09

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