WO2013091954A2 - Moteur électrique présentant une précontrainte axiale entre un palier à roulement et une partie de carter, ainsi qu'un procédé pour faire fonctionner un tel moteur électrique - Google Patents

Moteur électrique présentant une précontrainte axiale entre un palier à roulement et une partie de carter, ainsi qu'un procédé pour faire fonctionner un tel moteur électrique Download PDF

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Publication number
WO2013091954A2
WO2013091954A2 PCT/EP2012/071220 EP2012071220W WO2013091954A2 WO 2013091954 A2 WO2013091954 A2 WO 2013091954A2 EP 2012071220 W EP2012071220 W EP 2012071220W WO 2013091954 A2 WO2013091954 A2 WO 2013091954A2
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WO
WIPO (PCT)
Prior art keywords
axial
axially
spring elements
rotor shaft
spring
Prior art date
Application number
PCT/EP2012/071220
Other languages
German (de)
English (en)
Other versions
WO2013091954A3 (fr
Inventor
Thomas Singler
Alexander Ksoll
Mario Huesges
Alexander Kuderer
Juergen Herbst
Andreas Vathke
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 CN201280063513.6A priority Critical patent/CN103999334B/zh
Priority to EP12780716.2A priority patent/EP2795770A2/fr
Priority to KR1020147017147A priority patent/KR20140106598A/ko
Publication of WO2013091954A2 publication Critical patent/WO2013091954A2/fr
Publication of WO2013091954A3 publication Critical patent/WO2013091954A3/fr

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Classifications

    • 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
    • H02K7/081—Structural association with bearings specially adapted for worm gear drives
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K2205/00—Specific aspects not provided for in the other groups of this subclass relating to casings, enclosures, supports
    • H02K2205/03—Machines characterised by thrust bearings

Definitions

  • Electric machine with an axial bias between a rolling bearing and a housing part, and method for operating such an electric machine
  • the invention relates to an electric machine for driving functional elements in the motor vehicle with an axial preload between a housing part and a rolling bearing and of a method for operating such a machine according to the type of independent
  • Preload can only ever be applied between the disk set and designed as a floating bearing bearings. This embodiment is not suitable to apply a bias between the housing and the rolling bearing. In addition, the expert gets no hint how he can support higher axial forces with a small available space for the axial spring element.
  • the electric machine according to the invention as well as the inventive method for operating such a machine with the features of the independent claims have the advantage over the prior art that by forming at least two axially arranged in series spring elements using a small axial space sufficient axial prestress between the Housing of the electric machine and arranged on the rotor shaft bearings can be applied.
  • the serial arrangement of the at least two axial spring elements causes, in analogy to an electrical series circuit, the summation of the elastic spring forces of the individual axial spring elements in the axial direction.
  • Outer ring and the inner ring of a rolling bearing can be compensated, as well as the rotor shaft relative to the housing of the electric machine are subjected to a sufficient axial bias.
  • the invention is particularly advantageous for an axial bias on a as a
  • the inner ring of the rolling bearing is in this case fixedly arranged on the rotor shaft, so that a
  • the rolling bearing is suitable in the electric machine for receiving axially acting forces wherein the axial forces can be derived more or less damped over the outer ring to the housing.
  • the rolling bearing may be formed, for example, as a ball bearing or cylinder bearing, wherein the rolling elements (balls or cylindrical pins) roll between the inner ring and the outer ring. If the line of action of the axial force of the axially successively arranged spring elements engages directly in the region of the inner ring of the rolling bearing, shear forces between the rolling bearing and the rotor shaft are prevented.
  • the spring elements can lie directly axially on the inner ring, or else a contact disk between the inner ring and the spring element can be arranged. Due to the fixed fixation of the inner ring on the rotor shaft system-related component and manufacturing tolerances between the inner ring and the outer ring can be compensated by the inner ring is acted upon directly with a sufficient bias. To compensate for such an axial bearing clearance, the spring elements disposed axially one behind the other typically exert a preload with respect to the housing in the range of 50-150 N, preferably approximately 100 N.
  • the spring forces of axially successively arranged spring elements engage the outer ring of the rolling bearing, in which case the outer ring at least within certain limits in the axial direction movable in the
  • Axial forces up to 1500 N can be effective axially damped, whereby the mechanical load on the bearings and the rotor is significantly reduced.
  • the spring elements arranged axially in series on the outer ring act on the axial damping of the rotor and at the same time engage another elastic spring element on the inner ring in order to compensate for the axial bearing clearance within the rolling bearing.
  • the elastic spring element which acts on the inner ring as an integral part of the axially successively arranged spring elements which engage the outer ring formed.
  • the contact surface of the rotor shaft can be adapted to the point of application of the spring elements, for example, a plastic material can be arranged to increase the sliding action.
  • the invention finds application in an electrical machine which is designed as a transmission drive unit, for example, a
  • Windscreen wiper drives in the vehicle Here, a worm is mounted on the rotor shaft, which cooperates with a worm wheel. These together form a worm gear, which has an output shaft for a
  • Adjusting part provides. Due to the burden of
  • Worm gear can act on the screw large axial forces on the rotor shaft, which can be formed jerky in particular when switching the direction of rotation of the electric motor drive. Such axial load peaks can be effectively damped with the spring arrangement according to the invention.
  • the rolling bearing is arranged so that it can rotate and slide between the worm and the armature core of the rotor, since then the axial forces acting on the worm are damped axially as close as possible to its point of application.
  • the axially successively arranged spring elements may be formed as an integral, one-piece component or as separate components, which are either firmly connected to each other or loosely mounted to each other axially in the housing. It is essential that the individual axial spring elements of their action analogous to an electrical series circuit interact, the individual spring characteristics of the axial
  • Spring elements can be selected according to the axial forces occurring.
  • the spring elements are advantageously designed as disc springs or cup-shaped springs, which abut each other axially on their outer circumference or at a radially inner region or are interconnected.
  • two, three, four or more individual spring elements can be coupled together axially.
  • the individual spring elements advantageously have individual resilient components, which are arranged parallel to one another analogously to the electrical circuit. This means that the individual resilient components distributed over the circumference of the spring element provide individual axial spring forces which are simultaneously effective side by side, and whose axial forces act parallel to each other.
  • the individual resilient components are designed, for example, as spring webs which connect a radially outer region of the spring element to a radially inner region. In this case, for example, two, three, four or more resilient components in a single axial
  • the individual spring elements are formed with annular spring surfaces. That means in
  • each spring element has only a single resilient component, which is formed homogeneously over the entire circumference.
  • Spring element is formed for example by a plate spring, in the middle of which, for example, a hole is formed, and the annular spring surface is slightly conical.
  • the individual spring elements can be made particularly favorable as stamped parts, which are preferably cut out of a metal sheet.
  • a metal sheet for this purpose, in particular spring steel, wherein the thickness and the elasticity of the metal sheet, as well as the specific shape of the resilient webs, is optimally selected according to the applied bias.
  • both the axially successively arranged axial spring elements, as well as possibly the individual resilient webs with different spring constants be formed.
  • the spring characteristic over the axial deflection can be freely designed by material thickness and the shape of the spring element along its radial extent can be designed accordingly.
  • At least one additional floating bearing is arranged, which allows an axial relative movement of the rotor shaft relative to the housing.
  • a third or further bearing may be arranged, which are designed as movable bearings or support bearings. Due to the defined axial elastic support of the first bearing a reliable radial and axial bearing of the rotor can be ensured in combination with other movable bearings or support bearings, without over-determination of storage occurs.
  • the axially successively connected spring elements can be preassembled first favorable process in the housing of the electric machine, then then with the assembly of the rotor, the fixed arranged on the rotor shaft bearings under bias to the spring elements is applied.
  • the rolling bearing is preferably clamped during its assembly directly between the respective spring elements.
  • the spring elements arranged axially one behind the other on both sides of the roller bearing can be connected to one another by means of a bracket, so that the two-sided spring assemblies are formed as a one-piece component in the form of a clamping goggle.
  • the execution of such a clamping glasses can also be conveniently mounted with a process step after assembly of the arranged on the rotor shaft bearing to
  • Rotor shaft is deflected only slightly axially over a large axial force range.
  • Such a course of the spring characteristic can by the
  • Spring elements such as disc springs or pot springs are realized. Another possibility for realizing this spring characteristic is to punch out a single component in such a way that different individual spring components are combined to form a specific characteristic curve or axial axial spring elements arranged in series can be integratively combined in one component, in particular a bent stamped part.
  • the different ones Spring stiffnesses can also be generated locally by different sheet metal cross sections or different material thicknesses.
  • the method according to the invention for operating such an electrical machine has the advantage that disturbing stop noises of the electric drive unit can be effectively prevented. This is particularly important for drive units that are operated for a long time in Reversier Anlagen, such as a wiper direct drive or a
  • Rear wiper drive Due to the special design of the axial damping of the rolling bearing and / or the rotor shaft can be operated by utilizing a low axial space requirement with minimal noise, the transmission of the reversing drive utilizing an optimal efficiency. In this case, for example, when a change of direction first axial play within the rolling bearing damped compensated and then arranged axially in series spring elements with an increasing
  • stops are advantageously formed on the housing in the two axial directions, against which the rotor shaft bears axially when the axial forces are exerted. As a result, these high axial forces are transmitted from the armature shaft directly to the housing, without this, the rolling bearing is additionally loaded axially.
  • the rotor shaft performs the same mirror-symmetrical course of motion when subjected to an axial force in a first direction, as in the case of an application of an axial force in an opposite axial direction.
  • FIGS. 1 and 2 show two different embodiments of an electric machine according to the invention with following worm gears
  • FIG. 3 and Figure 5 are sections of two further invention
  • Figure 4 and Figure 6 shows two different individual axial spring elements for
  • Figure 7 shows a schematic arrangement of the individual spring elements on a
  • Figure 9 shows another embodiment of an inventive
  • FIG. 10 spring elements arranged axially one behind the other, as can be used for example in FIG. 9,
  • Figure 11 shows another embodiment of a transmission drive unit according to the invention.
  • Rolling bearing arranged spring elements.
  • an electric machine 10 is shown with a downstream transmission 12, which is formed for example as an electric motor drive unit 11.
  • a transmission drive unit 11 may, for example, for the adjustment of moving parts in the motor vehicle, such as
  • Windscreen wipers, window panes, sunroof or seat parts can be used.
  • the electric machine 10 has a rotor shaft 12 which is mounted in a housing part 16 of the housing 17 of the gear drive unit 11.
  • an anchor packet 24 is shown schematically, the For example, arranged in the housing 17 magnet 25th
  • a roller bearing 20 is arranged, which is formed in the embodiment as a ball bearing 22.
  • rolling elements 30 are arranged, which are formed as balls 31 in the ball bearing 22.
  • the inner ring 28 is fixedly fixed on the rotor shaft 12, so that a rotation or displacement of the inner ring 28 against the rotor shaft 12 is prevented.
  • This rotation and displacement-resistant connection can be realized for example by a press fit and / or a plastic material deformation between the rotor shaft 12 and the inner ring 28.
  • the outer ring 26 is fixed in the housing part 16 in a manner fixed against rotation and displacement.
  • the rolling bearing 20 is formed as a so-called fixed bearing 21, which can transmit in the axial direction 5 acting on the rotor shaft 12 forces on the housing part 16. It has thus the
  • a transmission element 40 is further arranged, which meshes with a corresponding gear 42 of the transmission 14.
  • a transmission element 40 is further arranged, which meshes with a corresponding gear 42 of the transmission 14.
  • Gear element 40 is formed as a screw 41, which is fixed rotationally and non-displaceably on the rotor shaft 12.
  • the worm 41 drives as a worm wheel
  • Spring elements 32 are arranged, which lie in the axial direction 5 to each other.
  • the axially successively arranged spring elements 32 cause a biasing force 34 which acts axially on the inner ring 28 in the axial direction 5 via the rotor shaft 12. Since the inner ring 28 is fixed against displacement on the rotor shaft 12, thus lies constantly a bias 34 between the inner ring 28 of the rolling bearing 20 and the housing part 16 at which the spring elements 32 are supported. As a result, the axial clearance of the rolling bearing 20 is eliminated, whereby the disturbing
  • Spring elements 32 are shown schematically in Fig. 1 and show the
  • the individual spring elements 32 have a plurality of resilient components 60, which are arranged parallel to each other in analogy to an electrical circuit and each have an axial
  • biasing force 34 to the rolling bearing 20.
  • the axially successively arranged spring elements 32 are for example pot-shaped or dish-shaped, so that a relatively high biasing force 34 can be generated in an axially small space within the housing part 16.
  • Embodiment in Fig. 1 has only a single roller bearing 20, which is preferably between the anchor assembly 24 and the transmission element 40 - in particular a screw 41 - is arranged.
  • a further radial bearing 50 is arranged, which is designed for example as a sliding bearing 51.
  • the further radial bearing 50 is arranged, for example, at the end 53 of the rotor shaft 12 on the rolling bearing 20 opposite side of the armature package 24.
  • a third radial bearing 54 is formed, which supports the rotor shaft 12 via a plain bearing bush 55 radially.
  • the radial bearings 50 and 54 allow a movement of the rotor shaft 12 in the axial direction 5 relative to the housing 17 and are therefore also referred to as a floating bearing.
  • the radial bearings 50, 54 are arranged axially displaceable on the rotor shaft 12 and fixed at its outer periphery in the housing part 16.
  • FIG. 2 shows a variation of the gear drive unit 11 according to FIG. 1, in which the roller bearing 20, on which the pretensioning force 34 acts, is arranged on the end 53 of the rotor shaft 12.
  • the inner ring 28 of the rolling bearing 20th rotatably and slidably connected to the rotor shaft 12, wherein the outer ring 26 is fixedly fixed in the housing part 16.
  • the axial bearing clearance of the bearing formed as a fixed bearing 20 occurs at the axial end 53 of the rotor shaft 12.
  • the biasing force 34 engages on
  • a concrete embodiment of this is shown in Figs. 5 and 6.
  • a second rolling bearing 23 is arranged between the armature core 24 and the worm 41, which in contrast to the embodiment according to FIG. 1, however, is preferably designed here as a floating bearing.
  • the outer ring 26 is arranged axially displaceably in the bearing seat 18.
  • the inner ring 28 can be arranged to be axially displaceable on the rotor shaft 12.
  • the transmission-side end 52 of the rotor shaft 12 is supported in this embodiment by a support bearing 56, which is to prevent deflection of the rotor shaft 12 away from the gear 42. If the transmission 14 is designed as a worm gear 15, during a transmission of a drive torque a
  • the housing part 16 is formed in the embodiments of Figure 1 and Figure 2, for example, as a pole pot 19 in which the armature core 24 of the electric motor 9 is mounted.
  • the pole pot 19 for example, an axial extension 29, in which a radial bearing 20, 50 is arranged.
  • the axially successively arranged spring elements 32 are also disposed within the axial extension 29 of the pole pot 19, wherein the axial length 27 of the axial extension 29 is to be minimized by the inventive design and arrangement of the spring elements 32.
  • FIG. 3 and FIG. 4 show a specific embodiment of the spring elements 32 which can be used, for example, for the spring elements 32 shown schematically in FIG. In Figure 3, for example, three individual spring elements 32 are shown, each lying axially directly adjacent to each other.
  • the spring elements 32 have a radially inner region 59, which in this exemplary embodiment is connected to the outer circumference 58 via individual resilient components 60.
  • the resilient components 60 are formed as spring webs 61 which extend spirally from the radially inner portion 59 to the outer periphery 58.
  • the spring elements 32 are each plate-shaped, or slightly conical.
  • the second and the third spring element 32 are each at its radially inner portion 59 axially against each other.
  • a biasing force 34 is generated between the housing part 16 and the rolling bearing 20, not shown here, wherein the biasing force 34 via the rotor shaft 12 on the inner ring 28 of the rolling bearing 20 (for example, according to Figure 1) acts.
  • the series-arranged spring elements 32 are in this case on the radially inner portion 59 on the rotor shaft 12, wherein a so-called startup mushroom 62 is arranged to improve the sliding properties at the end 53 of the rotor shaft.
  • the starting mushroom 62 is made of plastic, for example, which significantly reduces the friction between the rotor shaft 12 and the spring element 32 made of metal, for example.
  • the individual spring elements 32 can be loosely inserted into the housing part 16 during assembly, wherein this example, by a schematically illustrated guide sleeve 57 - which may optionally be integrated directly into the housing part 16 - are performed.
  • the individual spring elements 32 are each directly on the housing part 16 and on the rotor shaft 12, and each other directly.
  • further thrust washers, or connecting elements between the spring elements 32 and / or the housing part 16 and the rotor shaft 12 can be arranged in each case.
  • the individual spring elements 32 can be connected to one another in the axial direction 5 be so that instead of the individual spring elements 32, only a single spring assembly 64 - consisting of the axially arranged one behind the other
  • FIG. 5 and FIG. 6 show a further variant of spring elements 32 arranged axially one behind the other, as can be used, for example, in the exemplary embodiment according to FIG.
  • the rolling bearing 20 at the end of 53 of the rotor shaft 12 is arranged, so that the spring elements 32 directly to the
  • Inner ring 28 can act on a biasing force 34.
  • the radially inner portion 59 of the spring elements 32 has a circular recess 65 which, for example, at least the
  • Diameter 66 of the rotor shaft 12 corresponds.
  • the radially inner region 59 is in this case formed as a circular ring 67, which here is axially supported on the inner ring 28 of the rolling bearing 20.
  • the spring elements 32 are again plate-shaped or cup-shaped and lie on the outer circumference 58 to each other.
  • the outer periphery 58 is connected via resilient components 60 with the radially inner portion 59.
  • three spring webs 61 are shown in each case, which are formed with respect to the axial spring action as parallel to each other arranged resilient components 60.
  • the spring elements 32 of Figures 3 and 5 may also have four or five or more spring bars 61, or formed with respect to their circumferential direction as a homogeneously formed plate spring washers, as shown for example in Figures 9 and 10.
  • the radially inner region 59 can rotate relative to the outer circumference 58, as a result of which the spring travel is converted at least partially into a torsional movement by a pure axial movement.
  • the axial space of the housing part 16 can be reduced, wherein in Figure 5 two
  • Spring elements 32 are arranged axially in series, but in alternative
  • Embodiments also three, four or more spring elements 32 can be arranged axially one behind the other. Again, the individual spring elements 32 can optionally be mounted loosely to each other, or previously connected to a spring pact 64.
  • the contact surface of the spring package 64 on the housing part 16 can be done either at the radially inner portion 59 or at the outer periphery 58 (corresponds to a combination of Figure 3 to Figure 6).
  • the spring elements 32 may alternatively be formed of a non-metallic material, for example of plastic. In the arrangement of the spring elements 32 in the housing part 16, these can be fixed with respect to a rotational movement, a housing 17, or with the rotor shaft
  • spring elements 32 arranged axially one behind the other are arranged at both ends 52, 53 of the rotor shaft, their spring characteristics being able to be matched to one another.
  • the spring constants of the axially serially arranged spring elements 32 are identical for each spring element 32, whereby also the spring constants of the individual resilient elements
  • FIG. 7 shows a further exemplary embodiment in which a rotor shaft 12 is mounted in a housing 17 by means of a roller bearing 20.
  • the inner ring 28 is fixed against rotation and displacement on the rotor shaft 12, the outer ring 26 is arranged within certain limits along the axial direction 5 displaceable in the housing part 16.
  • On both opposite sides 70, 71 of the rolling bearing 20 at least two axially successively arranged spring elements 32 are arranged, on the one hand on the outer ring 26 and on the other hand on
  • Support housing part 16 axially. Now works for example over the
  • Transmission element 40 an axial force 6 on the rotor shaft 12 a
  • Spring elements 32 axially damped.
  • the spring characteristic of the axially successively arranged spring elements 32 is designed such that the springs are formed relatively stiff at low axial forces 6 and thereby the rolling bearing 20 is approximately not deflected with the rotor shaft 12. Only with a strong increase of the acting axial force 6, the spring stiffness decreases, whereby a greater deflection in the axial direction x is allowed.
  • These Damped deflection of the rotor shaft 12 takes place at high axial forces 6 until the rotor shaft 12 abuts with its end 52, 53 against an axial stop 72, 73.
  • the axially juxtaposed spring elements 32 are in
  • This course of the deflection X is plotted in FIG. 8 over the acting axial force F.
  • a positive force F acts on the rotor shaft 12 (to the right in FIG. 7, for example)
  • the rotor shaft 12 is first deflected along the deflection X parallel to the axial direction 5 until the axial play between the inner ring 28 and the outer ring 26 is eliminated Fi).
  • the axial force F is further increased, the rotor shaft 12 experiences practically no further further due to the special design according to the invention of the spring characteristic of the spring elements 32 arranged axially one behind the other
  • Axial stop 72 so that in a further increase in the force F, the mechanical load of the rolling bearing 20 is limited to F max , and the higher forces F are derived directly from the rotor shaft 12 to the axial stop 72. If the rotor shaft 12 with an axial force -F in
  • axial springs 74, 75 can also be arranged on the inner ring 28 for damping the axial bearing clearance, the region of which is illustrated in FIG. 8 between + Fi and - Fi.
  • These axial springs 74, 75 may be integrally arranged axially one behind the other on the outer ring 26
  • Be spring elements 32 or be formed as a separate axial springs, as shown for example in Figure 13.
  • the individual spring elements 32 are formed similarly to the embodiment according to FIG. 5 with an outer circumference 58 and an inner circular ring 67.
  • the spring elements 32 are in this case designed as disc springs which form a homogeneous circular ring 67 over the entire circumference in order to be able to absorb higher axial forces 6.
  • the individual spring elements 32 abut each other axially on the outer circumference 58 or on the radially inner region 59, so that in the exemplary embodiment preferably four spring elements 32 can be arranged axially in series. Alternatively, however, two, three or more than four spring elements 32 can be arranged axially one behind the other.
  • the housing part 16 hereby forms an integrated
  • Guide sleeve 57 is in which the spring elements 32 are guided in a deflection X of the rotor shaft 12 in the axial direction 6.
  • X deflection of the rotor shaft 12 in the axial direction 6.
  • Spring element 32 with its outer circumference 58 directly on the outer ring 26 of the rolling bearing 20 at. Another arranged in series spring element 32 lies with its outer periphery 58 axially on the housing part 16.
  • the bias voltage 34 of the symmetrical to the rolling bearing 20 arranged on both sides 70, 71 spring assemblies 64 can be adjusted by an axial fixing element 78, which is formed for example as a clamping ring 79 which engages in a circumferential groove 80.
  • a plurality of disc springs are summarized as axially successively arranged spring elements 32 to a spring assembly 64.
  • the individual spring elements 32 form an annular spring surface 82, which is slightly funnel-shaped towards the center.
  • the figure 8 underlying non-linear spring characteristic is realized that in these plate-shaped Springs the annular spring surface 82 is relatively stiff and initially not deformed at axial load initially, until the
  • spring elements 32 on both sides 70, 71 of the roller bearing 20 are designed to carry out the "series connection" of the spring elements 32 as compactly as possible, as an alternative to the juxtaposition of identical spring elements 32 in the axial direction 5, different spring elements 32 with different spring characteristics can also be arranged axially in series to be ordered.
  • spring washers 84 rest axially on the housing 17 on both sides 70, 71 of the roller bearing 20.
  • These spring washers 84 are for example mounted radially from one side of the rotor shaft 12, but in an alternative embodiment, not shown, but also be slid onto the rotor shaft 12 in an annular manner.
  • a bow spring 86 is arranged such that its two legs 87 on the one hand abut axially on the spring washers 84 and on the other hand are supported on both sides 70, 71 on the rolling bearing 20.
  • one leg 87 of the bow spring 86, together with one respective spring washer 84 is arranged axially in series.
  • these spring packs 64 on both sides 70, 71 of the
  • Rolling bearing 20 formed symmetrically to each other.
  • the bow spring 86 can hereby advantageously be radially mounted after assembly of the rotor shaft 12, whereby the rolling bearing 20 is clamped on both sides with a predefinable preload force 34 in the housing 17.
  • a predefinable preload force 34 in the housing 17 According to the illustrations in Figure 7 and Figure 8 can by the specific shape of the spring washers 84 and the bow spring 86 again a course of the deflection X upon exposure an axial force 6 can be realized, in which the armature shaft 12 is initially hardly deflected, whereby the meshing engagement between the worm 41 and the worm wheel 43 optimally interlocks in normal operation and this is ensured over the entire life. Only when higher forces occur, for example in the event of a jerky load, is the rotor shaft 12 deflected in a damped manner in order to protect the gear teeth from destruction.
  • the rolling bearing 20 is in turn formed as a fixed bearing between the armature core 24 and the transmission element 4, wherein at the end 53 of the rotor shaft 12 corresponding to the figure 1, a sliding bearing 51st
  • the electric motor 9 is commutated via a collector 88, which is energized via carbon brushes 89.
  • the armature package 24 of the electric motor 10 is arranged in the pole pot 19, which is connected to a transmission housing 90, in which the electronics 91 is received.
  • the inner ring 28 is fixed on the rotor shaft 12 so as to be non-displaceable. This is in this
  • Embodiment by means of plastic material deformation for example, two
  • Bow spring 86 are in the embodiment on their inner sides 85 directly on the outer ring 26.
  • the free ends 92 of the legs 87 are bent away from both sides of the rolling bearing 20 and are located on the two spring washers 84 axially.
  • the spring discs 84 are curved, such that the
  • Spring washers 84 are formed from the support point 93 of the free ends 92 axially away from the bearing surface on the housing 17 bent. Due to the radial mounting of the bow spring 86 is about the spring washers 84 an axial
  • Biasing force 34 exerted on the rolling bearing 20 The concrete course of the deflection X is the acting axial force F of Figure 8 then by the concrete shape of the bow spring 86 with the legs 87, and the design of the spring washers 84 are designed.
  • FIG. 13 shows a further embodiment in which spring elements 32 arranged axially in series are arranged on both sides 70, 71 of the roller bearing 20.
  • the axially successively formed spring elements 32 are each integrally formed as an integral spring member 94 which is axially on both sides 70, 71 of the rolling bearing 20 radially to the rotor shaft 12 can be mounted.
  • the integrated spring component 94 in this case has a first spring element 32, which is axially supported on the housing 17 with an axial web 95.
  • Spring element 32 is formed as a material taper 96 of the radially extending spring member 94, which is arranged axially in series with the axial web 95.
  • the axial web 95 is combined as a first spring element 32 with a high spring stiffness with the material taper 96 as a second spring element 32 with a low spring stiffness, which in turn a non-linear characteristic can be realized.
  • the integral spring member 94 is supported with a nose 97 on the outer ring 28, whereby the outer ring 26 attenuated within the housing 17 can move axially when exposed to high axial forces 6.
  • the contact surfaces of the integrated spring member 94 on the housing 17 may be formed differently depending on the application, so that over the extent of
  • Contact surfaces can also adjust the spring stiffness of the integrated spring member 94 (see differences in the left and right side of Figure 13).
  • the axial bearing play compensation spring tongues 98 are formed as axial springs 74, 75 according to the figure 7, which rest axially on the inner ring 28. In this embodiment, both the axial play can be compensated by the integrated spring member 94, as well as very high axial
  • Bracket be formed together as a one-piece component, which is radially mounted in a simple manner.
  • Embodiments are varied. For example, at one end 52, 53 of the armature shaft 12 or between the armature core 24 and the transmission element 40.
  • the combination with other bearings can be varied, which may be formed, for example, as a further rolling bearing 53, as a sliding bearing 51 or as a support bearing 56.
  • the axial bearing clearance spring forces of 100 N to 150 N are typically realized by the configuration of the axially arranged in series spring elements 32, for the damped deflection of the outer ring 26 in the housing 17 under the action of high axial force peaks, the axially successively arranged spring elements 32 typically for Spring forces up to 1500 N designed.
  • the different embodiments of the individual spring elements 32 can be exchanged for the different embodiments, wherein decisively determines the required spring forces and the available space as a concrete design of the individual spring elements 32.
  • the axial length of a single spring element is 0.5 to 1.5 mm.
  • the invention is particularly suitable for the adjustment of moving parts in
  • Winscreen wipers windows, sunroof, vehicle seat
  • windshield wipers windows, sunroof, vehicle seat

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  • Motor Or Generator Frames (AREA)

Abstract

L'invention concerne un moteur électrique (10), en particulier une unité d'entraînement à engrenage (11) pour entraîner des éléments fonctionnels dans un véhicule automobile, ainsi qu'un procédé pour faire fonctionner un tel moteur électrique (10), présentant un arbre (12) de rotor qui s'étend dans le sens axial (5) et qui est logé de manière pouvoir tourner au moyen d'un palier à roulement (22, 20) dans une partie (16) d'un carter (17). Au moins deux éléments (32) ressort axiaux sont disposés axialement l'un derrière l'autre. Les éléments (32) ressort axiaux sont disposés, en ce qui concerne leur effet de force, en série dans le sens axial (5) et s'appuient axialement sur la partie (16) de carter et exercent une précontrainte entre la partie (16) de carter et le palier à roulement (20, 22).
PCT/EP2012/071220 2011-12-23 2012-10-26 Moteur électrique présentant une précontrainte axiale entre un palier à roulement et une partie de carter, ainsi qu'un procédé pour faire fonctionner un tel moteur électrique WO2013091954A2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201280063513.6A CN103999334B (zh) 2011-12-23 2012-10-26 在滚动轴承与壳体件之间具有轴向的预应力的电机及用于运行这样的电机的方法
EP12780716.2A EP2795770A2 (fr) 2011-12-23 2012-10-26 Moteur électrique présentant une précontrainte axiale entre un palier à roulement et une partie de carter, ainsi qu'un procédé pour faire fonctionner un tel moteur électrique
KR1020147017147A KR20140106598A (ko) 2011-12-23 2012-10-26 롤링 베어링과 하우징부 사이에 축 방향 예비 응력을 갖는 전기 기계 및 상기 전기 기계의 작동 방법

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102011089855.7 2011-12-23
DE102011089855 2011-12-23
DE102012208972.1 2012-05-29
DE201210208972 DE102012208972A1 (de) 2011-12-23 2012-05-29 Elektrische Maschine mit einer axialen Vorspannung zwischen einem Wälzlager und einem Gehäuseteil, sowie Verfahren zum Betreiben einer solchen elektrischen Maschine

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WO2013091954A2 true WO2013091954A2 (fr) 2013-06-27
WO2013091954A3 WO2013091954A3 (fr) 2014-05-08

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PCT/EP2012/071220 WO2013091954A2 (fr) 2011-12-23 2012-10-26 Moteur électrique présentant une précontrainte axiale entre un palier à roulement et une partie de carter, ainsi qu'un procédé pour faire fonctionner un tel moteur électrique

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EP (1) EP2795770A2 (fr)
KR (1) KR20140106598A (fr)
CN (1) CN103999334B (fr)
DE (1) DE102012208972A1 (fr)
WO (1) WO2013091954A2 (fr)

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CN103762773A (zh) * 2013-12-31 2014-04-30 宁波菲仕运动控制技术有限公司 一种伺服电机的轴承轴向弹簧预紧结构
DE102016012032A1 (de) * 2016-10-11 2018-04-12 Grammer Aktiengesellschaft Gehäuse für einen elektrischen Antrieb
CN115098977A (zh) * 2022-07-20 2022-09-23 重庆大学 一种浮动支撑摩擦片组件冲击动载计算方法

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DE102014212133A1 (de) * 2014-06-25 2015-12-31 Robert Bosch Gmbh Antriebseinheit
CN104590955B (zh) * 2014-12-10 2016-10-05 徐工集团工程机械股份有限公司 自动张紧装置以及绳体长度测量装置
DE102016202958A1 (de) * 2016-02-25 2017-08-31 Robert Bosch Gmbh Elektrische Maschine, sowie Getriebe-Antriebseinheit enthaltend eine solche Maschine
DE102016117082A1 (de) * 2016-09-12 2018-03-15 HELLA GmbH & Co. KGaA Haltefeder für einen Aktor und Aktor
DE102016120356A1 (de) * 2016-10-25 2018-04-26 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Antriebsvorrichtung
DE102016225417A1 (de) 2016-12-19 2018-06-21 Robert Bosch Gmbh Lagereinrichtung für eine Welle und Antriebseinrichtung mit einer Lagereinrichtung
DE102017214116A1 (de) * 2017-08-11 2019-02-14 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Antriebsvorrichtung für einen Fensterheber
CN107643176B (zh) * 2017-10-30 2024-04-19 南京磁谷科技股份有限公司 一种超速试验台主机结构
DE102018009030A1 (de) * 2018-11-16 2020-05-20 Zf Active Safety Gmbh Lageranordnung
DE102019205246A1 (de) * 2019-04-11 2020-10-15 Robert Bosch Gmbh Wellenanordnung, Antriebseinheit und Arbeitsvorrichtung
CN110194210B (zh) * 2019-05-30 2021-08-31 奇瑞汽车股份有限公司 一种转向器的齿轮轴间隙调整结构
DE102019219218A1 (de) * 2019-12-10 2021-06-10 Robert Bosch Gmbh Elektrischer Antrieb
DE102020201957A1 (de) * 2020-02-17 2021-08-19 Scanlab Gmbh Galvanometerantrieb mit spielfreier Lagerung
KR102563341B1 (ko) * 2020-12-30 2023-08-07 계양전기 주식회사 텐션부재를 포함하는 전동모터

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DE102016012032A1 (de) * 2016-10-11 2018-04-12 Grammer Aktiengesellschaft Gehäuse für einen elektrischen Antrieb
CN115098977A (zh) * 2022-07-20 2022-09-23 重庆大学 一种浮动支撑摩擦片组件冲击动载计算方法

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EP2795770A2 (fr) 2014-10-29
KR20140106598A (ko) 2014-09-03
WO2013091954A3 (fr) 2014-05-08
CN103999334B (zh) 2018-09-11
DE102012208972A1 (de) 2013-06-27
CN103999334A (zh) 2014-08-20

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