DE4224980A1 - Electromotor for driving high pressure pump of brake installation of motor vehicle - has drive shaft preloaded in lengthways direction from driven pump to motor - Google Patents

Electromotor for driving high pressure pump of brake installation of motor vehicle - has drive shaft preloaded in lengthways direction from driven pump to motor

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Publication number
DE4224980A1
DE4224980A1 DE4224980A DE4224980A DE4224980A1 DE 4224980 A1 DE4224980 A1 DE 4224980A1 DE 4224980 A DE4224980 A DE 4224980A DE 4224980 A DE4224980 A DE 4224980A DE 4224980 A1 DE4224980 A1 DE 4224980A1
Authority
DE
Germany
Prior art keywords
shaft
drive shaft
motor
electric motor
housing
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Withdrawn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
DE4224980A
Other languages
German (de)
Inventor
Josef Lauer
Christoph Wagner
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
ITT Automotive Europe GmbH
Alfred Teves 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 ITT Automotive Europe GmbH, Alfred Teves GmbH filed Critical ITT Automotive Europe GmbH
Priority to DE4224980A priority Critical patent/DE4224980A1/en
Publication of DE4224980A1 publication Critical patent/DE4224980A1/en
Withdrawn legal-status Critical Current

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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
    • B60T8/40—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
    • B60T8/4018—Pump units characterised by their drive mechanisms
    • B60T8/4022—Pump units driven by an individual electric motor
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
    • H02K5/1732—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at both ends of the rotor
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/083—Structural association with bearings radially supporting the rotary shaft at both ends of the rotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Power Engineering (AREA)
  • Transportation (AREA)
  • Support Of The Bearing (AREA)

Abstract

The electromotor (1) has bearings at both ends. A drive shaft (8) drives a radial load dependent on rotational angle. The drive shaft is preloaded in a lengthways direction from the driven pump (6) to the motor. Pref., the drive shaft (8) is mounted in the motor housing (2, 3) by two roller bearings (9, 10). ADVANTAGE - Reduced running noise since axial forces transferred to the bearings do not change their direction.

Description

Die Erfindung betrifft einen durch Vorspannung an der Motor­ welle geräuscharm gelagerten Elektromotor, insbesondere zum Antrieb einer Hochdruckpumpe für Kfz-Bremsanlagen.The invention relates to a by biasing the motor wave low-noise electric motor, especially for Drive a high pressure pump for vehicle brake systems.

Überlicherweise sind Elektromotoren an den Enden der Motor­ welle über zwei Wälzlager im Motorgehäuse gelagert. Weiter­ hin ist regelmäßig eine elastische Abstützung vorgesehen, die einem Hereindrücken des einen Verbraucher antreibenden Wellenstummels in das Motorgehäuse federnd entgegenwirken. Bei einem derartigen Aufbau eines Motors treten Schwierig­ keiten auf, wenn eine größere Kraft quer zum Wellenstummel wirkt. In diesem Falle wird die Welle über den Stummel und die beiden Lager gekrümmt, so daß innerhalb des Motors die Motorwelle eine Krümmung aufweist, die der am Stummel an­ greifenden Kraft entgegengerichtet ist. Gleichzeitig kann man beobachten, daß dabei die beiden Motorenden und insbe­ sondere das stummelseitige Ende der Motorwelle um ein Stück in das Gehäuse hereingezogen wird. Hierbei entstehen in Richtung der Wellenlängsachse wirkende Kräfte an den Wälzla­ gern, wobei die Wälzlager, die somit auch axial gerichtete Kräfte aufnehmen müssen. Beim Auftreten derartiger Axial­ kräfte verschieben sich die Lagerringe der Wälzlager gegen­ einander, wodurch sich auch die Bahn der Kugeln auf den La­ gerringen ändert. Electric motors are usually at the ends of the motor shaft is supported by two roller bearings in the motor housing. Next an elastic support is regularly provided, that pushing a consumer in Counteract the shaft end in the motor housing. With such a structure of an engine, there are difficulties come up when there is a greater force across the shaft stub works. In this case the shaft is over the stub and the two bearings are curved so that the inside of the motor Motor shaft has a curvature that at the stub opposing force is directed. At the same time one observes that the two motor ends and esp especially the stub end of the motor shaft by a piece is pulled into the housing. Here arise in Forces acting on the Wälzla in the direction of the longitudinal axis like, the roller bearings, which are thus also axially directed Have to absorb forces. When such an axial occurs Forces the bearing rings of the rolling bearings move against each other, which also causes the orbits of the balls to wrestles changes.  

Eine derartige Änderung der Kräfte in den Wälzlagern führt zu Geräuschbildungen. Dies ist insbesondere dann der Fall, wenn die Richtung der auf den Wellenstummel wirkenden Ra­ dialkräfte sich periodisch ändert. Dies ist beispielsweise beim Antrieb einer Hochdruckpumpe mit zwei oder mehr Kolben durch einen Elektromotor der Fall.Such a change in the forces in the rolling bearings leads to noise. This is particularly the case if the direction of the Ra acting on the shaft stub dial forces change periodically. For example, this is when driving a high pressure pump with two or more pistons by an electric motor.

Ein besonderer Nachteil der üblichen axialen Vorspannung bei Elektromotoren besteht darin, daß die übliche elastische Ab­ stützung als Vorspannung der weiter oben beschriebenen Kraft entgegenwirkt, welche versucht durch die Krümmung der Welle diese in den Motor hineinzuziehen, was, wie schon erwähnt, bei radialer Belastung des Wellenstummels der Fall ist. Die­ se beiden Kräfte können sich aufheben, so daß das bei jedem Lager vorhandene Spiel sich wieder in axialer Schwingung auswirken kann. Der Zweck der Vorspannung, einen ruhigeren Lauf des Elektromotors zu gewährleisten, ist somit nicht mehr gegeben. In diesem Fall kann es passieren, daß der Mo­ tor trotz Vorspannung besonders unruhig läuft und die peri­ odisch auf den Wellenstummel auswirkenden Querkräfte relativ laute Geräusche verursachen.A particular disadvantage of the usual axial preload Electric motors is that the usual elastic Ab support as a preload of the force described above counteracts which tries through the curvature of the wave pulling them into the engine, which, as already mentioned, is the case with radial loading of the shaft stub. The se two forces can cancel each other out, so that with each Bearing existing play again in axial vibration can impact. The purpose of bias, a quieter It is therefore not possible to ensure that the electric motor runs given more. In this case it can happen that the Mo gate runs particularly unsteady and the peri transverse forces acting on the shaft stub relative make loud noises.

Die Erfindung geht daher aus von einem Elektromotor der sich aus dem Oberbegriff des Anspruchs 1 ergebenden Gattung und hat sich zur Aufgabe gestellt, mit einfachen Mitteln das Ge­ räuschverhalten eines derartigen Motors erheblich zu verbes­ sern.The invention is therefore based on an electric motor genus resulting from the preamble of claim 1 and has set itself the task of using simple means noise behavior of such an engine to verbes considerably ser.

Die Aufgabe wird durch die sich aus dem kennzeichnenden Teil des Anspruchs 1 ergebende Merkmalskombination gelöst. Die Erfindung besteht im Prinzip also darin, die Lager wellen­ seitig in der gleichen Richtung vorzuspannen, in der auch die Kräfte wirken, die durch die periodisch auftretenden, drehwinkelabhängigen radial auf den Wellenstummel einwirken­ den Kräfte bewirkt werden. Diese Lösung ist generell für al­ le Arten der Motorlagerung für die gattungsgemäßen Motoren zweckmäßig, soweit diese einen in axialer Richtung wirkenden Anschlag besitzen, der eine Axialbewegung der Welle be­ grenzt.The task is characterized by the characteristic part of the combination of features resulting from claim 1. The In principle, the invention therefore consists in undulating the bearings  pretension in the same direction in the same way the forces act through the periodically occurring act on the stub shaft depending on the angle of rotation the forces are brought about. This solution is generally for al le types of engine mounting for the generic engines expedient, as far as this one acting in the axial direction Have stop that be an axial movement of the shaft borders.

Eine besonders zweckmäßige Ausgestaltung des Motors ergibt sich nach Anspruch 2, da hier die Erfindung auf besonders reibungsarm laufende Motoren anwendbar wird.A particularly expedient design of the engine results itself according to claim 2, since here the invention in particular low-friction engines can be used.

Um die erfindungsgemäße Wirkung zu unterstützen, empfiehlt sich bei mit Wälzlagern versehenen Motoren die Verwendung der Merkmalskombination nach Anspruch 3. Dabei wird die Steifigkeit des Gehäuses dazu ausgenutzt, beide Lager in axialer Richtung vorzuspannen.To support the effect according to the invention, it is recommended use in motors equipped with roller bearings the combination of features according to claim 3 Rigidity of the housing used to both bearings in preload in the axial direction.

Eine besonders einfache Abstützung für die vorspannende Fe­ der an der Welle ist durch die Merkmale nach Anspruch 4 auf­ gezeigt. Durch die Vorspannung beider Wälzlager über das in sich steife Gehäuse mittels einer einzigen Feder läßt sich auch eine Entlastung des Gehäuses bei einem Gehäuseaufbau erreichen, wie er gemäß Anspruch 5 aufgeführt ist.A particularly simple support for the prestressing Fe which is on the shaft by the features of claim 4 shown. By preloading both roller bearings over the in can be rigid housing by means of a single spring also relieves the load on the housing when the housing is being constructed achieve as listed in claim 5.

Ein Ausführungsbeispiel der Erfindung wird nachfolgend an­ hand der Zeichnung erläutert.An embodiment of the invention is described below hand of the drawing explained.

Die in der Zeichnung dargestellten Bauelemente werden nur insoweit näher erklärt, als sie für die Erfindung wesentlich sind. Die Zeichnung zeigt einen Elektromotor 1 mit einer er­ sten Gehäuseschale 2 und einer zweiten Gehäuseschale 3. An die zweite Gehäuseschale 3 kann, wie durch die symbolisch angedeuteten Schraubverbindungen 4 und 5 gezeigt, eine Hoch­ druckpumpe 6 angeflanscht sein, die auf einen aus dem Gehäu­ se 1 hervorragenden Wellenstummel 7 einwirkt. Unter der Vor­ aussetzung, daß der Motor zwei Kolben besitzt, wird der ex­ zentrisch zur Welle 8 angeordnete Wellenstummel 7 abwech­ selnd durch die Kraft K1 und K2 in radialer Richtung beauf­ schlagt, so daß die Welle 8 zwischen den Wälzlagern 9 und 10 abwechselnd eine nach oben bzw. unten gerichtete Krümmung aufweist, die jeden inneren Lagerringe der Wälzlager 9 und 10 in axialer Richtung in das Motorgehäuse 2, 3 hineinzuzie­ hen versucht. Dementsprechend werden auch axiale Kräfte auf die äußeren Lagerringe der Wälzlager 9 und 10 ausgeübt, die aufgrund ihres periodischen Auftretens zu entsprechenden pe­ riodischen Schlägen führen, welche sich als schwingendes oder klopfendes Geräusch bemerkbar machen. Dies ist insbe­ sondere auch deshalb der Fall, weil senkrecht zur Ebene des Betrachters keine Kraft auf den Wellenstummel 7 wirkt und dieser sich somit zwischen der Wirkung der beiden Kräfte. K1, K2 immer wieder entspannt.The components shown in the drawing are only explained in so far as they are essential to the invention. The drawing shows an electric motor 1 with a housing shell 2 and a second housing shell 3 . To the second housing shell 3 , as shown by the symbolically indicated screw connections 4 and 5 , a high-pressure pump 6 can be flanged, which acts on a shaft stub 7 projecting from the housing 1 . Under the prerequisite that the engine has two pistons, the ex-centrally arranged to the shaft 8 stub shaft 7 alternately strikes by the force K1 and K2 in the radial direction, so that the shaft 8 between the bearings 9 and 10 alternately one after has upward or downward curvature that hen each inner bearing rings of the roller bearings 9 and 10 axially in the motor housing 2 , 3 tries to hen. Accordingly, axial forces are exerted on the outer bearing rings of the roller bearings 9 and 10 , which, due to their periodic occurrence, lead to corresponding periodic impacts which are noticeable as an oscillating or knocking noise. This is particularly the case because perpendicular to the viewer plane no force acts on the shaft end 7 and this is thus between the action of the two forces. K1, K2 always relaxed.

Während nun bei der üblichen Vorspannung des Motors eine Kraft, wie oben beschrieben, auf die den inneren Lagerringen wirkenden Kraft entgegenwirkt, ist nach der Erfindung die Vorspannung derart gewählt, daß sie in der gleichen Richtung wie die Kräfte wirkt, welche die inneren Wälzlagerringe ver­ suchen nach innen zu ziehen.While now with the usual engine bias Force, as described above, on the inner bearing rings counteracting force is according to the invention Bias chosen so that it is in the same direction how the forces act, which ver the inner rolling bearing rings looking to pull inside.

Hierzu ist eine Feder 11 vorgesehen, die sich zum einen an einem Anschlag 12 auf der Welle 8 und zum anderen an dem in­ neren Lagerring des Wälzlagers 9 abstützt. Der innere Lager­ ring 13 des Wälzlagers 9 ist auf der Welle 8 axial ver­ schieblich gelagert, so daß durch die Kraft der Feder 11 die Welle 8 um ein Stück aus dem Gehäuse 2, 3 herausgezogen wer­ den kann. Bei einer derartigen Bewegung der Welle 8 in der Zeichnung nach links, wird der innere Lagerring 14 des Wälz­ lagers 10 nach links mitgenommen. Das kann beispielsweise dadurch geschehen, daß der Lagerring 14 fest auf der Welle 8 sitzt oder aber, daß, wie in der Zeichnung dargestellt, ein entsprechender Sicherungsring 15 die innere Lagerschale 14 mitnimmt. Damit wird der Abstand der beiden inneren Lager­ ringe 13, 14 vermindert, so daß aufgrund der Steifigkeit des Gehäuses 2, 3 die beiden inneren Lagerringe 13, 14 gegenüber den entsprechenden äußeren Lagerringen der Wälzlager 9, 10 sich in Richtung zum Gehäuseinneren hin verschieben. Damit sind die beiden Wälzlager in der gleichen Richtung vorge­ spannt, wie sie auch senkrecht durch die Kräfte K1 und K2 beaufschlagt werden. Als Folge davon laufen die Kugeln der Wälzlager 9 und 10 bei den beiden Innenringen 13, 14 ständig an der Außenkante der Kurvenbahn, während die Kugeln hin­ sichtlich der zugehörigen Außenringe auf der Innenkante der Kugelbahn laufen.For this purpose, a spring 11 is provided, which is supported on the one hand on a stop 12 on the shaft 8 and on the other on the inner bearing ring of the rolling bearing 9 . The inner bearing ring 13 of the roller bearing 9 is axially slidably mounted on the shaft 8 so that the force of the spring 11, the shaft 8 is pulled out a bit from the housing 2 , 3 who can. With such a movement of the shaft 8 in the drawing to the left, the inner bearing ring 14 of the roller bearing 10 is taken to the left. This can happen, for example, in that the bearing ring 14 sits firmly on the shaft 8 or that, as shown in the drawing, a corresponding locking ring 15 takes the inner bearing shell 14 with it. So that the distance between the two inner bearing rings 13 , 14 is reduced, so that due to the rigidity of the housing 2 , 3, the two inner bearing rings 13 , 14 relative to the corresponding outer bearing rings of the roller bearings 9 , 10 move towards the interior of the housing. So that the two bearings are preloaded in the same direction, as they are also acted upon vertically by the forces K1 and K2. As a result, the balls of the roller bearings 9 and 10 in the two inner rings 13 , 14 run continuously on the outer edge of the cam track, while the balls visibly run the associated outer rings on the inner edge of the ball track.

Dabei können die auftretenden axialen Lagerkräfte aufgrund der wirksamen Querkräfte K1, K2 zwar schwanken, aber nicht ihre Richtung ändern, was beträchtlich zu der Laufruhe der Lager beiträgt. Entsprechendes gilt für die Verbindungsstel­ len der beiden Lagerschalen 2 und 3, die ebenfalls durch die Feder 11 auf Druck vorgespannt sind und somit bei hinrei­ chend großer Vorspannung ebenfalls durch die abwechselnd ziehende und drückende Kraft aufgrund der Wirkung von K1 und K2 nicht in unterschiedlichen Richtungen bewegt werden. The axial bearing forces occurring can fluctuate due to the effective transverse forces K1, K2, but they cannot change their direction, which contributes considerably to the smooth running of the bearings. The same applies to the connecting points len of the two bearing shells 2 and 3 , which are also biased by the spring 11 to pressure and thus also with sufficient preload by the alternating pulling and pressing force due to the effect of K1 and K2 not moved in different directions will.

Hinsichtlich der Lagerung der Feder ist aus der Zeichnung noch zu ersehen, daß sich der Anschlag 12 durch einen Bund einer in das Ende der Welle 8 eingeschraubten Schraube 16 ergibt. Weitere Möglichkeiten, die Federkraft am Wellenende aufzubringen, sind denkbar. Die weiteren aus der Zeichnung ersichtlichen Bauelemente des Motors 1, wie Wicklung auf der Welle, Stromzuführung über Schleifkontakte, Sensor, Lei­ tungszuführung und ähnliches, sollen an dieser Stelle nicht erörtert werden, da diese Baugruppen mit der Erfindung nicht in unmittelbarem Zusammenhang stehen.With regard to the mounting of the spring, it can still be seen from the drawing that the stop 12 results from a collar of a screw 16 screwed into the end of the shaft 8 . Other options for applying the spring force to the shaft end are conceivable. The other apparent from the drawing components of the motor 1 , such as winding on the shaft, power supply via sliding contacts, sensor, Lei line supply and the like should not be discussed at this point, since these modules are not directly related to the invention.

Claims (5)

1. Elektromotor (1) mit an den beiden Motorenden gelagerter, eine drehwinkelabhängige Radialbelastung aufnehmender An­ triebswelle, insbesondere zum Antrieb eines Verbrauchers in Form einer Hochdruckpumpe für Kfz-Bremsanlagen, da­ durch gekennzeichnet, daß die Antriebs­ welle (8) in einer von dem angetriebenen Verbraucher (6) zum Motor (1) hin weisenden Längsrichtung vorgespannt ist.1. Electric motor ( 1 ) mounted on the two motor ends, a rotational angle-dependent radial load receiving drive shaft, in particular for driving a consumer in the form of a high-pressure pump for vehicle brake systems, characterized in that the drive shaft ( 8 ) in one of the driven Consumer ( 6 ) is biased towards the motor ( 1 ) pointing in the longitudinal direction. 2. Elektromotor nach Anspruch 1, dadurch gekenn­ zeichnet, daß die Antriebswelle (8) im Motorge­ häuse (2, 3) über zwei Wälzlager (9, 10) gelagert ist.2. Electric motor according to claim 1, characterized in that the drive shaft ( 8 ) in the motor housing ( 2 , 3 ) via two roller bearings ( 9 , 10 ) is mounted. 3. Elektromotor nach Anspruch 2, dadurch gekenn­ zeichnet, daß zur Erzeugung der Vorspannung (V) eine Feder (11) an dem dem Verbraucher abgewandten Wel­ lenende (12, 16) und dem zugeordneten auf der Welle sit­ zenden Lagerring (13) des zugehörigen Wälzlagers (9) an­ greift, daß die Welle (8) zumindest gegenüber diesem La­ gerring (13) verschiebbar ist, daß die Welle (8) in bezug auf den gegenüberliegenden in­ neren Lagerring (14), beispielsweise über einen Anschlag (15), in Vorspannrichtung (V) unverschiebbar ist und daß die äußeren Lagerringe gegenüber dem Gehäuse (2, 3) im we­ sentlichen unverschiebbar sind. 3. Electric motor according to claim 2, characterized in that for generating the bias voltage (V) a spring ( 11 ) on the consumer facing away from len end ( 12 , 16 ) and the associated on the shaft sit Zenden bearing ring ( 13 ) of the associated Rolling bearing ( 9 ) engages that the shaft ( 8 ) at least with respect to this La gerring ( 13 ) is displaceable, that the shaft ( 8 ) with respect to the opposite in other bearing ring ( 14 ), for example via a stop ( 15 ), in the biasing direction (V) is immovable and that the outer bearing rings relative to the housing ( 2 , 3 ) are essentially immovable. 4. Elektromotor nach Anspruch 3, dadurch gekenn­ zeichnet, daß die Feder (11) über eine in das Wellenende eingeschraubte Anschlagmutter (16) oder ähnli­ che formschlüssige Verbindung an der Welle (8) angreift.4. Electric motor according to claim 3, characterized in that the spring ( 11 ) engages via a screwed into the shaft end stop nut ( 16 ) or similar surface positive connection on the shaft ( 8 ). 5. Elektromotor nach einem der vorangegangenen Ansprüche, dadurch gekennzeichnet, daß das Motorge­ häuse (2, 3) aus zwei ineinandergefügten Gehäuseschalen (2, 3) besteht.5. Electric motor according to one of the preceding claims, characterized in that the Motorge housing ( 2 , 3 ) consists of two nested housing shells ( 2 , 3 ).
DE4224980A 1992-07-29 1992-07-29 Electromotor for driving high pressure pump of brake installation of motor vehicle - has drive shaft preloaded in lengthways direction from driven pump to motor Withdrawn DE4224980A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE4224980A DE4224980A1 (en) 1992-07-29 1992-07-29 Electromotor for driving high pressure pump of brake installation of motor vehicle - has drive shaft preloaded in lengthways direction from driven pump to motor

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE4224980A DE4224980A1 (en) 1992-07-29 1992-07-29 Electromotor for driving high pressure pump of brake installation of motor vehicle - has drive shaft preloaded in lengthways direction from driven pump to motor

Publications (1)

Publication Number Publication Date
DE4224980A1 true DE4224980A1 (en) 1994-02-03

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DE4224980A Withdrawn DE4224980A1 (en) 1992-07-29 1992-07-29 Electromotor for driving high pressure pump of brake installation of motor vehicle - has drive shaft preloaded in lengthways direction from driven pump to motor

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Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996009682A1 (en) * 1994-09-23 1996-03-28 Itt Automotive Europe Gmbh Electric motor, pump and an electric motor/pump unit
DE19653638A1 (en) * 1996-12-20 1998-06-25 Teves Gmbh Alfred Electric motor and pump assembly
FR2785466A1 (en) * 1998-10-29 2000-05-05 Valeo Equip Electr Moteur Vehicle alternator assembly for automobile, has a trued cylindrical rotor to reduce generated noise
EP0944774B1 (en) * 1996-12-23 2000-09-13 Continental Teves AG & Co. oHG Deep groove ball bearing
DE19959022C1 (en) * 1999-12-08 2001-06-21 Bosch Gmbh Robert Drive unit for hydraulic pressure source e.g. for automobile servo steering system, has electric motor enclosed by separate motor hood anchored to flange plate of pressure source
FR2849547A1 (en) * 2002-12-27 2004-07-02 Mitsubishi Electric Corp ELECTRO-HYDRAULIC SERVO-STEERING DEVICE
WO2005107044A1 (en) * 2004-04-29 2005-11-10 Siemens Aktiengesellschaft Electrical machine and its bearings
EP1631743A2 (en) * 2003-04-14 2006-03-08 Hargraves Technology Corporation Pump motor with bearing preload
DE102007049209A1 (en) * 2007-02-05 2008-08-07 Continental Teves Ag & Co. Ohg DC motor
WO2011144323A1 (en) * 2010-05-19 2011-11-24 Eppendorf Ag Vibration damping for an electric device
DE102012215284A1 (en) 2012-06-18 2013-12-19 Continental Teves Ag & Co. Ohg roller bearing assembly
DE102013203991A1 (en) 2013-01-16 2014-07-17 Continental Teves Ag & Co. Ohg bearing assembly
DE102013218119A1 (en) 2013-07-23 2015-03-12 Continental Teves Ag & Co. Ohg bearing assembly

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DE608532C (en) * 1928-11-20 1935-01-25 Berko Werke Quast & Co Device for adjusting the air gap in small magneto-electric machines
CH240887A (en) * 1944-10-23 1946-01-31 Oerlikon Maschf Device for resiliently limiting the longitudinal play of the shaft of small electrical machines running in roller bearings
DE1207482B (en) * 1964-07-28 1965-12-23 Michael Winter Fabrik Fuer Fei Low-noise, small electric motor with a ball-bearing shaft
DE3524360A1 (en) * 1984-08-07 1986-02-20 VEB Kombinat Robotron, DDR 8010 Dresden Silenced mounting of the shaft in stepper motors
CH657725A5 (en) * 1981-04-14 1986-09-15 Papst Motoren Kg ARRANGEMENT FOR SUPPRESSING AXIAL ROTOR VIBRATIONS IN AN ELECTRIC SMALL MOTOR.
US5061868A (en) * 1989-09-25 1991-10-29 Nippon Densan Corporation Spindle motor

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE608532C (en) * 1928-11-20 1935-01-25 Berko Werke Quast & Co Device for adjusting the air gap in small magneto-electric machines
CH240887A (en) * 1944-10-23 1946-01-31 Oerlikon Maschf Device for resiliently limiting the longitudinal play of the shaft of small electrical machines running in roller bearings
DE1207482B (en) * 1964-07-28 1965-12-23 Michael Winter Fabrik Fuer Fei Low-noise, small electric motor with a ball-bearing shaft
CH657725A5 (en) * 1981-04-14 1986-09-15 Papst Motoren Kg ARRANGEMENT FOR SUPPRESSING AXIAL ROTOR VIBRATIONS IN AN ELECTRIC SMALL MOTOR.
DE3524360A1 (en) * 1984-08-07 1986-02-20 VEB Kombinat Robotron, DDR 8010 Dresden Silenced mounting of the shaft in stepper motors
US5061868A (en) * 1989-09-25 1991-10-29 Nippon Densan Corporation Spindle motor

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996009682A1 (en) * 1994-09-23 1996-03-28 Itt Automotive Europe Gmbh Electric motor, pump and an electric motor/pump unit
US5742109A (en) * 1994-09-23 1998-04-21 Itt Automotive Europe Gmbh Electric motor, pump and an electric motor/pump system
DE19653638A1 (en) * 1996-12-20 1998-06-25 Teves Gmbh Alfred Electric motor and pump assembly
EP0944774B1 (en) * 1996-12-23 2000-09-13 Continental Teves AG & Co. oHG Deep groove ball bearing
FR2785466A1 (en) * 1998-10-29 2000-05-05 Valeo Equip Electr Moteur Vehicle alternator assembly for automobile, has a trued cylindrical rotor to reduce generated noise
DE19959022C1 (en) * 1999-12-08 2001-06-21 Bosch Gmbh Robert Drive unit for hydraulic pressure source e.g. for automobile servo steering system, has electric motor enclosed by separate motor hood anchored to flange plate of pressure source
FR2849547A1 (en) * 2002-12-27 2004-07-02 Mitsubishi Electric Corp ELECTRO-HYDRAULIC SERVO-STEERING DEVICE
US7217106B2 (en) 2002-12-27 2007-05-15 Mitsubishi Denki Kabushiki Kaisha Electro-hydraulic power steering apparatus
EP1631743A4 (en) * 2003-04-14 2006-12-20 Hargraves Technology Corp Pump motor with bearing preload
CN100499316C (en) * 2003-04-14 2009-06-10 哈格雷夫斯技术公司 Pump motor with bearing preload
EP1631743A2 (en) * 2003-04-14 2006-03-08 Hargraves Technology Corporation Pump motor with bearing preload
DE102004021138A1 (en) * 2004-04-29 2005-11-24 Siemens Ag Electric machine and its bearings
WO2005107044A1 (en) * 2004-04-29 2005-11-10 Siemens Aktiengesellschaft Electrical machine and its bearings
US7604414B2 (en) 2004-04-29 2009-10-20 Siemens Aktiengesellschaft Electrical machine and its bearings
DE102007049209B4 (en) 2007-02-05 2023-12-14 Continental Automotive Technologies GmbH DC motor
DE102007049209A1 (en) * 2007-02-05 2008-08-07 Continental Teves Ag & Co. Ohg DC motor
WO2011144323A1 (en) * 2010-05-19 2011-11-24 Eppendorf Ag Vibration damping for an electric device
US8791609B2 (en) 2010-05-19 2014-07-29 Eppendorf Ag Vibration damping for an electric device
CN102918752B (en) * 2010-05-19 2015-07-22 埃佩多夫股份公司 Vibration damping for an electric device
CN102918752A (en) * 2010-05-19 2013-02-06 埃佩多夫股份公司 Vibration damping for an electric device
DE102012215284A1 (en) 2012-06-18 2013-12-19 Continental Teves Ag & Co. Ohg roller bearing assembly
DE102013203991A1 (en) 2013-01-16 2014-07-17 Continental Teves Ag & Co. Ohg bearing assembly
DE102013218119A1 (en) 2013-07-23 2015-03-12 Continental Teves Ag & Co. Ohg bearing assembly

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