EP1563188A1 - Ensemble moteur-pompe - Google Patents

Ensemble moteur-pompe

Info

Publication number
EP1563188A1
EP1563188A1 EP03810968A EP03810968A EP1563188A1 EP 1563188 A1 EP1563188 A1 EP 1563188A1 EP 03810968 A EP03810968 A EP 03810968A EP 03810968 A EP03810968 A EP 03810968A EP 1563188 A1 EP1563188 A1 EP 1563188A1
Authority
EP
European Patent Office
Prior art keywords
motor
bearing
pump unit
channel
unit according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP03810968A
Other languages
German (de)
English (en)
Inventor
Dieter Dinkel
Thomas Bartsch
Sven Martin
Rüdiger BRIESEWITZ
Axel Niescher
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.)
Continental Teves AG and Co OHG
Original Assignee
Continental Teves AG and Co OHG
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 Continental Teves AG and Co OHG filed Critical Continental Teves AG and Co OHG
Priority to EP06123309A priority Critical patent/EP1746288A3/fr
Publication of EP1563188A1 publication Critical patent/EP1563188A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/36—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition including a pilot valve responding to an electromagnetic force
    • B60T8/3615—Electromagnetic valves specially adapted for anti-lock brake and traction control systems
    • B60T8/3675—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units
    • B60T8/368—Electromagnetic valves specially adapted for anti-lock brake and traction control systems integrated in modulator units combined with other mechanical components, e.g. pump units, master cylinders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0443—Draining of the housing; Arrangements for handling leaked fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/006—Crankshafts

Definitions

  • the present invention relates to a motor-pump unit for a motor vehicle brake system, with a motor and with a pump, which comprises a shaft driven by the motor, the shaft end of which is rotatably mounted in at least one bearing in a receiving body provided with valves and connecting channels, wherein the shaft drives displacement means, which are arranged at least partially in a pressure-fillable space in which the bearing runs at least partially, and wherein the shaft end opens into a free space.
  • Such a motor-pump unit is known for example from DE 199 27 658 AI.
  • a motor vehicle brake system is filled with the necessary pressure medium after assembly of the individual system components such as, in particular, a master brake cylinder, a pipe and hose line system, the motor-pump unit and wheel brakes at the vehicle manufacturer.
  • the entire brake system is evacuated in a first process step in order to supply the pressure medium provided in a second process step.
  • roller bearing arrangements of motor-pump assemblies are exposed to high stresses, which are not typical for roller bearings, particularly during the pressure medium filling process.
  • high stresses which are not typical for roller bearings, particularly during the pressure medium filling process.
  • Overpressurization can result in the sealing of rolling elements such as sealing lips being knocked out. This in turn can Lubricant washout and consequently reduce pump life.
  • the bearings fail prematurely, which is particularly problematic in brake systems with long pump running times, such as, in particular, electro-hydraulic brake systems. Unsealed bearings have free access to the rolling surfaces and do not allow the use of a special lubricant. This is problematic if the lubricating properties of the pressure medium used are insufficient, or if the pressure medium contains wear products which can cause tread damage.
  • the invention is based on the object of providing an improved motor-pump unit in which the risk of bearing damage and lubricant leaching from bearings is reduced.
  • the bearing separates the space from the free space, and that a connection is provided between the space and the free space, which acts as a bypass to bypass the interior of the rolling bearing, so that neither lubricant leaching nor damage to the sealant are to be feared.
  • sealed roller bearings that are protected against lubricant washout can be used. Nevertheless, a quick and therefore inexpensive pressure medium filling process is made possible.
  • the free space and the space for receiving pressure medium, in particular for receiving leakage pressure medium are provided, a channel also being provided between a pressure medium storage container and the space, so that the free space is connectable to the pressure medium reservoir, in particular for filling purposes.
  • a channel also being provided between a pressure medium storage container and the space, so that the free space is connectable to the pressure medium reservoir, in particular for filling purposes.
  • the bearing is designed as a floating bearing in such a way that the connection between free space and space takes place via a gap between a bearing inner ring and a bearing seat.
  • connection is designed as a channel, the wall of which consists of peripheral regions of the inner ring and bearing seat.
  • the channel can basically have any cross-section and enables the connection mentioned at a defined point.
  • the bearing seat for forming the channel has at least one flattened portion, this can be attached simply by machining during the manufacture of the shaft. This avoids bypass holes on the housing side. The space saved in the housing as a result can be used for other purposes.
  • the shaft has an eccentric for driving at least one pump piston
  • the maximum of the eccentricity and the channel are arranged essentially in alignment with one another in relation to an axial direction. With this arrangement, the surface pressure on the bearing inner ring reduced because the available contact area is not reduced by the channel.
  • the bearing is arranged in a stepped through-bore of the receiving body, the bearing adjoining the free space, and the through-bore and the free space are provided with a closure.
  • the production of a through hole is simple compared to a blind hole and also enables the shaft end to be supported when mounting a motor-side bearing.
  • the closure is preferably designed as a cover, which rests on a bore step, and the cover is caulked to the receiving body.
  • the lid can be manufactured as a deep-drawn or pressed part and the caulking on the housing also reduces the manufacturing costs. In principle, tool-free clinching between the cover and the receiving body is possible without departing from the invention. It is important to ensure that the cover has a suitable profile and is made of a harder material than the receptacle.
  • the motor-pump unit has a driving motor shaft which is rotatably mounted in the receiving body with at least one bearing.
  • the bearing is arranged between a bearing plate of the engine and the crankcase.
  • the shaft drives displacement means that extend into the crankcase.
  • the absorbable leakage volume is further increased by the channel opening into a chamber which is delimited by the end shield and the receiving body, the chamber being connected to the leakage drain channel.
  • FIG. 1 shows a section through an embodiment of a motor-pump unit on a larger scale
  • Fig. 2 is a sketch for the schematic illustration of the location of the eccentric and channel
  • Fig. 3 shows a solution in which a side facing away from the crank chamber is connected to a leakage drain channel by a bearing via a channel.
  • a motor-pump unit 1 for use in a motor vehicle brake system is connected on the one hand to wheel brakes (not shown) and on the other hand to an encoder (not shown) such as a master brake cylinder with a pressure medium reservoir.
  • a receiving body 2 has at least six hydraulic connections.
  • the unit is particularly suitable and intended for electrohydraulic brake systems which have a high-pressure accumulator integrated on or in the receiving body 2, which serves to supply the wheel brakes.
  • the master brake cylinder is only in the Emergency used for brake actuation and primarily serves to simulate brake actuation forces.
  • the motor-pump unit 1 also contains a pump 3 for supplying the high-pressure accumulator or for supplying wheel brakes and a motor 4 for driving the pump 3.
  • An electronics unit 14 for controlling and regulating the system is located on a side opposite the motor 4 of the receiving body 2, wherein electronic control and supply lines of the motor 4 are passed through the receiving body 3.
  • the motor 4 drives a pump shaft 5, which is rotatably arranged within a stepped through bore 6 by means of sealed bearings 7, 8.
  • Bearing 7 is designed as a fixed bearing, while bearing 8 is designed as a floating bearing and therefore cannot absorb any axial forces.
  • the pump shaft 5 acts on displacement means for the pressure medium.
  • the preferred exemplary embodiment shown is a radial piston pump which, as a displacement means, has pump pistons 9, 10 which open into a space 11 arranged approximately centrally between the bearings 7, 8 and an eccentric connected to the shaft (not in the drawing) shown) are driven.
  • the number of pump pistons is arbitrary, with 3 pistons being preferred because this reduces pulsations and noise.
  • a roller bearing 12, in particular a needle bearing, is arranged between the eccentric and the pump piston 9, 10 for the purpose of reducing friction.
  • a channel opens into the space 11 13, which is connected to the pressure medium reservoir.
  • a shaft end 15 facing away from the motor extends into a free space 16 and passes through a bottom 17, which is inserted into the through bore 6, and rests axially on an outer ring of the bearing 8. There is a gap between the shaft 5 and a through hole through the bottom 17 for the passage of pressure medium.
  • An inner ring of the bearing 8 is arranged in the sliding seat on a shaft-side bearing seat 18, and there is a connection 19 between the space 11 and the free space 16.
  • the connection is designed as a channel 20, the wall of which consists of peripheral regions of the inner ring and bearing seat.
  • the bearing seat 18 has a flat 21, while the inner ring remains ring-shaped, so that between these adjacent components there is a crescent-shaped, free channel cross section for pneumatic evacuation and pressure medium passage.
  • Eccentricity and channel 20 are arranged in alignment with one another for an unchanged good bearing seat in the axial direction, as can be seen from FIG. 2.
  • the flattened portion 21 is essentially in the same angular position as the eccentric maximum (maximum stroke), as is illustrated by a dash-dotted line in FIG. 2. Because the maximum bearing forces are displaced in the displacement stroke on the side opposite the eccentric maximum (from the perspective of the bearing inner ring), there is no reduction in the effective, force-transmitting area at the bearing seat despite channel 20. This prevents damage to the bearing seat.
  • the flattening 21 can in principle be replaced by providing bores which extend through the interior of the shaft.
  • the free space 16 is provided with a closure 22 designed as a cover, which prevents a loss of pressure medium on the side of the electronics unit 14.
  • the cover is placed on a bore step 23 of the through bore 6 and caulked to the receiving body 2 in a liquid-tight and gas-tight manner.
  • a sealing element 25 is provided between the eccentric and the bearing 7 in the region of the motor-side shaft end 24, which is arranged in a holding body 26, so that no leakage liquid can get out of the receiving body 2 in the direction of the motor 4.
  • FIG. 3 shows an embodiment according to another solution in a so-called flying bearing with a freely projecting shaft end.
  • flying storage is widely used in motor-pump units of vehicle brake systems.
  • the known constructions suffer from the disadvantage that alternate heating and cooling processes - in particular from the engine - can to some extent cause an intake process, so that leakage fluid, which is located in the crankcase, can get into the engine interior as a result of a pressure difference. Damage to the bearing lubricant filling or flushing out of the lubricant as well as damage to the bearing sealant is possible.
  • FIG. 3 components and features that correspond to FIGS. 1 and 2 are provided with identical reference numerals. A repetition of the description in this regard is dispensed with in order to be able to go into the differences in detail below.
  • a pump shaft is used for the pump drive 5 with an eccentric, which is arranged in the crank chamber 11.
  • the end shield 30 is made of plastic material, closes the cup-shaped motor housing and temporarily supports the sealed bearing 7 before the final assembly of the motor 4 and the receiving body 2 by an annular connection piece 31 encompassing part of the outer bearing ring.
  • the crank chamber 11 is connected to a leakage drain channel 32, which can discharge accumulated leakage liquid into a storage chamber 33 of the unit 1, store it, or, for example, discharge it into the environment.
  • the receiving body 2 can have a tube 34 which extends into the storage chamber 33, with an outlet opening of the tube 34 is arranged at a distance from the free liquid level.
  • the side of the bearing 7 facing away from the crankcase is over one or several channels 13 connected to the leakage drain channel 32.
  • the ring connector 31 has one or more channels 13 which extend in the direction of the bearing seat facing away from the crank space in the bearing plate 30, so that contact with the intermediate space 35 can be produced, which is located between a bulkhead of the bearing plate 30 and the side of the bearing 7 facing away from the crank chamber.
  • Each channel 13 connects this side facing away from the crankcase to the leakage drain channel 32, which discharges leakage liquid - which can accumulate in the crankcase 11 and the intermediate space 35 - either into the environment or into the storage chamber 33.
  • the features described protect the interior of the engine in the area of the shaft exit against the ingress of leakage fluid. Even if leakage liquid should get through the bearing 7, it can be supplied to the leakage circuit which is provided anyway.
  • the system and in particular the bearing 7 is pneumatic from the point of view of the connection to the
  • the channel 13 can also be provided as a partial recess in the receiving body 2, as can be seen from FIG. 3.
  • the channel 13 can also be provided on an outer bearing ring, but this requires separate processing of this standardized component.
  • the channels 13 are provided in the receiving body 2.
  • the channel 13 does not have to open directly into the leakage drain channel 32. Because a chamber can be interposed, which is delimited by the bearing plate 30 and the receiving body 2.
  • the invention with an extremely compact design, enables the motor 4 to be greatly improved against leakage fluid while avoiding residues of water and / or leakage fluid (brake fluid) within the unit.
  • the invention can be applied to a wide variety of pump types which have a so-called internal leakage.
  • the invention is also suitable for use in connection with a gear pump, which has, for example, internal gear pairs as displacement means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Transportation (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)

Abstract

L'invention concerne un ensemble moteur-pompe (1) destiné au système de freinage d'un véhicule automobile et comprenant un moteur (4) et une pompe (3) qui comporte un arbre (5) entraîné par le moteur (4), l'extrémité (15) de l'arbre étant montée pivotante dans un corps logement (2) pourvu de soupapes et de canaux de liaison, par au moins un palier (8). L'arbre (5) entraîne des moyens de déplacement qui sont logés dans un compartiment (11) pouvant être rempli d'un agent de pression. Pour améliorer le remplissage sous vide du système de freinage d'un agent de pression, l'extrémité d'arbre (15) aboutit dans un espacement (16) et au moins une liaison (9) est installée entre l'espacement (16) et le compartiment (11).
EP03810968A 2002-11-11 2003-11-06 Ensemble moteur-pompe Withdrawn EP1563188A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06123309A EP1746288A3 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10252622 2002-11-11
DE10252622A DE10252622A1 (de) 2002-11-11 2002-11-11 Motor-Pumpen-Aggregat
PCT/EP2003/012363 WO2004044427A1 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP06123309A Division EP1746288A3 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Publications (1)

Publication Number Publication Date
EP1563188A1 true EP1563188A1 (fr) 2005-08-17

Family

ID=32185540

Family Applications (2)

Application Number Title Priority Date Filing Date
EP06123309A Withdrawn EP1746288A3 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe
EP03810968A Withdrawn EP1563188A1 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP06123309A Withdrawn EP1746288A3 (fr) 2002-11-11 2003-11-06 Ensemble moteur-pompe

Country Status (5)

Country Link
US (1) US7293495B2 (fr)
EP (2) EP1746288A3 (fr)
JP (2) JP2006505743A (fr)
DE (1) DE10252622A1 (fr)
WO (1) WO2004044427A1 (fr)

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Publication number Priority date Publication date Assignee Title
JP4267557B2 (ja) * 2004-10-29 2009-05-27 トヨタ自動車株式会社 ころ軸受およびそれを内蔵したポンプ
US20090263258A1 (en) * 2007-02-27 2009-10-22 Sauer-Danfoss Inc. Vibration dampening media in hydraulic power units
DE102008029536B4 (de) * 2008-04-28 2023-07-20 Continental Automotive Technologies GmbH Hydraulikaggregat
DE102008037047A1 (de) 2008-05-15 2009-11-19 Continental Teves Ag & Co. Ohg Hydraulikaggregat
US20100047097A1 (en) * 2008-08-20 2010-02-25 Protonex Technology Corporation Roller vane pump with integrated motor
US20100047088A1 (en) * 2008-08-20 2010-02-25 Protonex Technology Corporation Roller vane pump with integrated motor
JP5353139B2 (ja) * 2008-09-17 2013-11-27 株式会社アドヴィックス ブレーキ圧制御装置
JP5719213B2 (ja) * 2011-03-30 2015-05-13 株式会社ケーヒン 圧縮機
DE102011085288A1 (de) * 2011-10-27 2013-05-02 Continental Teves Ag & Co. Ohg Hydraulikaggregat
JP6395149B2 (ja) * 2014-08-04 2018-09-26 日立オートモティブシステムズ株式会社 ブレーキ液圧制御装置
DE102015222286A1 (de) * 2015-11-12 2017-05-18 Robert Bosch Gmbh Hydraulikblock und Hydraulikaggregat
CN109075651A (zh) 2016-05-04 2018-12-21 博泽沃尔兹堡汽车零部件有限公司 用于制造磁极壳体的方法
JP6876323B2 (ja) * 2017-02-03 2021-05-26 応研精工株式会社 モーター付きポンプ
TWI632305B (zh) * 2017-10-13 2018-08-11 建準電機工業股份有限公司 軸承組及具軸承組之馬達
IT201800009042A1 (it) * 2018-10-01 2020-04-01 Lyra Bearing Srl “pompa migliorata”

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JPS59160870U (ja) * 1983-04-15 1984-10-27 トヨタ自動車株式会社 ポンプの軸支持装置
JPS6228522A (ja) * 1985-07-29 1987-02-06 Aisin Seiki Co Ltd 流体機器の軸受構造
AT394892B (de) * 1989-09-18 1992-07-10 Tech Hydraulikgeraete Ges M B Radialkolbenpumpe
DE4241827A1 (de) * 1992-12-11 1994-06-16 Teves Gmbh Alfred Geräuschreduziertes Pumpenaggregat, insbesondere für geregelte Bremsanlagen
DE4433972A1 (de) * 1994-09-23 1996-03-28 Teves Gmbh Alfred Elektromotor, Pumpe sowie ein Elektromotor/Pumpenaggregat
DE4445362A1 (de) * 1994-12-20 1996-06-27 Bosch Gmbh Robert Kolbenpumpe
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JPH11103559A (ja) * 1997-09-26 1999-04-13 Aisin Seiki Co Ltd 駆動装置
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US6682325B1 (en) * 1999-12-01 2004-01-27 Continental Teves Ag & Co., Ohg Hydraulic unit
DE10023947A1 (de) 2000-05-16 2001-11-22 Bosch Gmbh Robert Wälzlager, Kolbenpumpe und Pumpenaggregat
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See references of WO2004044427A1 *

Also Published As

Publication number Publication date
DE10252622A1 (de) 2004-05-27
EP1746288A3 (fr) 2009-03-04
JP2006505743A (ja) 2006-02-16
US7293495B2 (en) 2007-11-13
WO2004044427A1 (fr) 2004-05-27
JP2011058499A (ja) 2011-03-24
US20060056995A1 (en) 2006-03-16
JP5431279B2 (ja) 2014-03-05
EP1746288A2 (fr) 2007-01-24

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