EP1476936A1 - Dispositif pour fixer un aimant torique sur un arbre d'induit - Google Patents

Dispositif pour fixer un aimant torique sur un arbre d'induit

Info

Publication number
EP1476936A1
EP1476936A1 EP02782718A EP02782718A EP1476936A1 EP 1476936 A1 EP1476936 A1 EP 1476936A1 EP 02782718 A EP02782718 A EP 02782718A EP 02782718 A EP02782718 A EP 02782718A EP 1476936 A1 EP1476936 A1 EP 1476936A1
Authority
EP
European Patent Office
Prior art keywords
arrangement according
armature shaft
ring magnet
spring
fastening arrangement
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Withdrawn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
EP02782718A
Other languages
German (de)
English (en)
Inventor
Andreas Wehrle
Helmut Meier
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.)
Robert Bosch GmbH
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
Priority claimed from DE10212507A external-priority patent/DE10212507A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1476936A1 publication Critical patent/EP1476936A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01P—MEASURING LINEAR OR ANGULAR SPEED, ACCELERATION, DECELERATION, OR SHOCK; INDICATING PRESENCE, ABSENCE, OR DIRECTION, OF MOVEMENT
    • G01P3/00—Measuring linear or angular speed; Measuring differences of linear or angular speeds
    • G01P3/42—Devices characterised by the use of electric or magnetic means
    • G01P3/44—Devices characterised by the use of electric or magnetic means for measuring angular speed
    • G01P3/48—Devices characterised by the use of electric or magnetic means for measuring angular speed by measuring frequency of generated current or voltage
    • G01P3/481—Devices characterised by the use of electric or magnetic means for measuring angular speed by measuring frequency of generated current or voltage of pulse signals
    • G01P3/487—Devices characterised by the use of electric or magnetic means for measuring angular speed by measuring frequency of generated current or voltage of pulse signals delivered by rotating magnets
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K23/00—DC commutator motors or generators having mechanical commutator; Universal AC/DC commutator motors
    • H02K23/66—Structural association with auxiliary electric devices influencing the characteristic of, or controlling, the machine, e.g. with impedances or switches

Definitions

  • the present invention relates to a
  • ring magnets are used to determine the rotor speed and direction of rotation. These ring magnets are on the
  • Armature shaft of the motor attached.
  • the magnets are exposed to both high thermal and mechanical loads.
  • the ring magnet is usually glued to the armature shaft for attachment to it. This process meets the high thermal and mechanical
  • the fastening arrangement according to the invention for fastening a ring magnet on an armature shaft of an electrical machine has the advantage that it can compensate for the different thermal expansions of the components that occur during operation. Furthermore, the fastening arrangement according to the invention is simple in construction and can be manufactured and assembled inexpensively. In addition, non-destructive disassembly of the
  • the fastening arrangement according to the invention is constructed in such a way that the ring magnet bears against a component arranged on the armature shaft on a first end face and bears against a fastening element arranged on the armature shaft on its opposite second end face.
  • the fastening element exerts a prestressing force on the ring magnet in the axial direction, ie in the axial direction of the armature shaft. As a result, the ring magnet is pressed against the component which is fixedly arranged on the armature shaft.
  • the fastening element is arranged on the armature shaft with preload in the radial direction, ie in the radial direction of the armature shaft.
  • the ring magnet is resiliently pressed against a component arranged fixedly on the armature shaft and can thus compensate for axial thermal expansions, in particular of the ring magnet.
  • the fastening element is also arranged resiliently in the radial direction on the armature shaft, so that in addition to compensating for changes in length in the axial direction, it can also compensate for changes in length in the radial direction and radial centering on the armature shaft is made possible.
  • the fastening element according to the invention thus provides a double resilient compensation acting in two different directions (axial and radial direction).
  • the ring magnet can also be arranged loosely, in particular with a close clearance fit, on the armature shaft and rotates in due to the pretension exerted by the fastening element
  • Axial direction with the armature shaft with. This also ensures non-destructive disassembly, so that individual components can be recycled or individual damaged components can be replaced without e.g. the entire assembly "armature shaft" must be replaced.
  • the fastening element is preferably designed as an adapter sleeve with a cylinder region and a flange region.
  • the flange area is arranged approximately perpendicular to the cylinder area and sets the preload in
  • the cylinder area provides the preload in the radial direction of the armature shaft.
  • one or more spring elements are preferably arranged on the flange area and / or on the cylinder area of the clamping sleeve.
  • the spring elements are particularly preferred as spring tongues or resilient projecting areas in the form of Beading formed so that the spring elements are integral parts of the clamping sleeve.
  • the fastening element can be designed as a one-piece component.
  • the fastening element is preferably non-positively and / or positively connected to the ring magnet or the armature shaft.
  • the ring magnet can be a flat contact surface for the
  • the prestressing force applied by the fastening element in the axial direction on the ring magnet is so great that there is no relative rotation between the ring magnet and the component which is arranged on the armature shaft when accelerating or decelerating.
  • a simple and inexpensive construction of the components can thus be provided.
  • projections and / or recesses can be provided on the ring magnet or the armature shaft, in which correspondingly formed spring tongues of the fastening element engage.
  • a positive connection between the ring magnet and the fastening element can reliably rule out a relative rotation between the armature shaft and the ring magnet.
  • a connection between the armature shaft and the fastening element is particularly preferably made possible only by means of a non-positive connection.
  • the fastening element is formed in two parts. This includes
  • Fastening element an adapter sleeve and a spring washer.
  • the adapter sleeve sets the preload in the axial direction ready and the spring ring provides the preload in the radial direction.
  • the spring ring is preferably arranged in the interior of the clamping sleeve, so that the spring ring lies between the armature shaft and the clamping sleeve.
  • the spring ring of the two-part fastening element preferably has a slot that is continuous in the axial direction.
  • the preload in the radial direction is preferably provided by a plurality of outwardly directed, resilient projections (beads).
  • Such a spring ring can be produced in a simple and inexpensive manner, for example by reshaping a spring plate.
  • the spring ring has at its two ends lying in the axial direction a plurality of spring tongues distributed around its circumference, which provide the preload force in the radial direction.
  • the clamping sleeve preferably has at its end opposite the flange area an extension directed inwards in the radial direction.
  • Shaft shoulder provided, which serves as a stop for the fastener or the two components in a two-part fastener.
  • the fastening arrangement is preferably used in a commutator motor and the component which is arranged in a stationary manner on the armature shaft is the commutator of the electrical machine or a shaft shoulder in the armature shaft.
  • a particularly space-saving construction results in the axial direction if the component which is fixedly arranged on the armature shaft is a section of the fastening element and the section and the fastening element are connected via a
  • a support area for the ring magnet is preferably provided, which has at least one tab, which protrudes at least obliquely from the armature shaft, for the
  • Ring magnets on ice Good centering results if the first end face of the ring magnet has a conical inner region.
  • the section has at least one spring element, which is supported on the armature shaft and serves to prevent rotation and / or axial locking, wherein preferably a plurality of spring elements are arranged, which preferably adjoin the tabs.
  • Figure 1 is a schematic, partially sectioned
  • Figure 2 is a sectional side view of the
  • FIG. 2 a front view of the fastening element shown in FIG. 2,
  • Figure 4 is a perspective view of a ring magnet, which by means of the invention
  • FIG. 5 is a front view of the ring magnet shown in FIG. 4,
  • Figure 6 is a partially sectioned side view of a
  • Figure 7 is a sectional side view of an adapter sleeve of the fastener according to the second
  • Figure 8 is a front view of that shown in Figure 7
  • Figure 10 is a front view of that shown in Figure 9
  • Figure 11 is a sectional side view of a fastening arrangement according to a third
  • Figure 12 is a sectional side view of a
  • FIG. 13 is a front view of a fastening arrangement according to a fifth embodiment of the present invention
  • Figure 14 is a schematic, partially sectioned
  • FIG. 15 shows a front view of the tensioning element from FIG. 14.
  • a fastening arrangement 1 according to a first exemplary embodiment of the present invention is described below with reference to FIGS. 1 to 5.
  • the fastening arrangement 1 is provided for fastening a ring magnet 2 on an armature shaft 3 of an electrical machine.
  • the ring magnet 2 is used to determine a speed of the armature shaft 3 and / or the direction of rotation of the armature shaft 3.
  • the armature shaft 3 is arranged centrally in a stator (not shown) and is mounted in the stator housing by means of bearings. For reasons of a simplified representation, only one bearing 10 is shown in FIG.
  • the fastening arrangement comprises a fastening element 4, which is shown in detail in FIGS. 2 and 3.
  • the fastening element 4 comprises a cylinder region 5 and a flange region 6.
  • the cylinder region 5 serves to fasten the fastening element 4 on the armature shaft 3.
  • inward projections (beads) are formed on the cylinder region 5, which act as spring elements 8 are provided in order to provide a spring or pretensioning force in the radial direction R of the cylinder region 5.
  • the clamping sleeve 4 is preferably made of a spring plate. As can also be seen from FIGS.
  • a Preloading force in the axial direction A of the clamping sleeve is provided by three spring tongues 7 (see FIG. 3), which are provided on a vertical flange region 6 of the clamping sleeve 4 and protrude from the clamping sleeve 4 in the axial direction. 5
  • the spring tongues 7 are in direct contact with the ring magnet 2 and press the ring magnet 2 against the commutator 9 (see FIG. 1).
  • a plurality of V-shaped recesses 12 are formed in the ring magnet 2, which for a
  • the 20 spring tongues 7 can simply be punched out on areas
  • the number of spring tongues 7 and the number of spring elements 8 can be chosen as desired. It only has to be ensured that sufficient pretensioning force is provided in the axial or radial direction.
  • an outer cylindrical region 11, which has improved stability, is additionally provided on the tensioning element 4 provides the adapter sleeve 4 and simplifies the assembly of the completed armature in the pole housing.
  • Cylinder region 5 of the clamping sleeve 4 also a stationary positioning of the clamping sleeve 4 on the armature shaft 3.
  • the spring elements 8 are designed such that they extend over the entire length of the cylinder region 5. However, it is also possible that they run only over one or more partial areas of the cylinder area 5 of the clamping sleeve 4.
  • the clamping sleeve 4 is positioned on the armature shaft 3 by means of a frictional connection.
  • a shaft projection 13 rolled onto the armature shaft 3 serves to fix the bearing 10 on the armature shaft.
  • a pretensioning force can be provided both in the axial direction A and in the radial direction R, which makes it possible to compensate for heat-related changes in size of the armature shaft 3 or the ring magnet 2.
  • the ring magnet 2 is pressed with its first end face S t against the commutator 9, the clamping sleeve 4 engaging on its second end face S 2 .
  • the inventive clamping sleeve 4 can compensate for changes in length of the commutator and / or the ring magnet 2 in the axial direction.
  • a fastening arrangement 1 according to a second exemplary embodiment of the present invention is described below with reference to FIGS. 6 to 10.
  • Fastening arrangement of the second exemplary embodiment is no longer formed from a one-piece fastening element, but from ⁇ in ⁇ m two-piece fastening element. More precisely, the fastening element of the second exemplary embodiment is formed from a clamping sleeve 24 and a spring ring 14. The clamping sleeve 24 is shown in more detail in FIGS. 7 and 8 and the spring ring 14 is shown in more detail in FIGS. 9 and 10. As can be seen from FIGS. 7 and 8, the clamping sleeve 24 according to the second exemplary embodiment only provides an axial biasing force
  • This pretensioning force in the axial direction A is provided as in the first exemplary embodiment by three punched-out and shaped spring tongues 7, which are distributed evenly on the circumference of the flange region 6 of the clamping sleeve 24.
  • the biasing force in the radial direction R is provided by the spring ring 14.
  • the spring ring 14 has for this purpose a multiplicity of beads 16 formed on its outer circumference, which press against the circular-cylindrical cylinder region 5 of the clamping sleeve 24.
  • the clamping sleeve 24 serves to provide the axial preload and the spring ring 14 serves to provide the radial preload.
  • a stop 17 is formed on the clamping sleeve 24 at the end opposite the flange region 6.
  • the stop 17 serves to position the spring ring 14 and to stiffen the clamping sleeve 24 in the cylindrical region.
  • a slot 15 is provided on the spring ring 14, which has a width D which corresponds approximately to the width of one of the beads 16 on the spring ring 14.
  • beads 16 on the spring ring 14 can of course also be formed on the inner circumference of the spring ring, or can be formed on both the inner and the outer circumference of the spring ring 14.
  • the fastener according to the invention according to the second embodiment also enables compensation for heat-related changes in length in the radial direction and in the axial direction. Since preferably the
  • Armature shaft and the spring washer are made of steel, a balance is only required between components with different coefficients of thermal expansion.
  • the fastening element according to the second exemplary embodiment is again formed in two parts from an adapter sleeve 24 and a spring ring 14.
  • the spring ring 14 ensures a non-positive connection of the fastening element to the armature shaft 3.
  • spring tongues 18 and 19 are provided on the two ends of the spring ring arranged in the axial direction, which in the form of a Many protruding areas or beads are provided.
  • the plurality of spring tongues 18 and 19 are preferably distributed uniformly around the circumference of the spring ring 14.
  • the clamping sleeve 24 provides the axial prestressing force in this exemplary embodiment only by means of a non-positive connection to a side S 2 of the ring magnet 2.
  • the third exemplary embodiment corresponds to the previously described exemplary embodiments, so that reference can be made to the description given there.
  • FIG. 12 shows a fastening arrangement according to a fourth exemplary embodiment of the present invention.
  • the same or functionally identical parts are again identified by the same reference numerals as in the previous exemplary embodiments.
  • a positive connection is provided between the clamping sleeve 24 and the ring magnet 2 by means of a spring-loaded element 7.
  • the spring-loaded elements 7 are offset in the axial direction, with the spring ring 14 and the clamping sleeve 24 remaining stationary on the armature shaft.
  • the spring-loaded, form-fitting connection between the ring magnet 2 and the clamping sleeve 24 again resets the element 7 to its starting positions.
  • the spring ring 14 is designed like the spring ring shown in FIGS. 9 and 10.
  • the elements 7 are always resilient elements which, on the one hand and for the function of the length compensation as a result of different thermal expansion
  • the function of the entrainment is useful when accelerating or decelerating the anchor. Otherwise, this exemplary embodiment corresponds to the preceding exemplary embodiments, so that reference is made to the description given there.
  • FIG. 13 shows a fastening arrangement according to a fifth exemplary embodiment of the present invention.
  • the same or functionally identical parts are identified with the same reference numerals as in the previous exemplary embodiments.
  • a plurality of spring elements 7, 7 ' are provided in the fifth exemplary embodiment, which are provided on the flange region 6 for the non-positive and positive connection with one side of the ring magnet 2.
  • the fastening element is again formed in two parts from a clamping sleeve 24 and a spring ring 14.
  • the spring tongues 7, 7 'again provide a biasing force in the axial direction, while the spring ring 14 provides a biasing force in the radial direction.
  • this embodiment corresponds to the previous embodiments, so that a detailed
  • FIG. 14 shows a further embodiment of a fastening arrangement.
  • This fastening arrangement according to the invention is also provided for fastening a ring magnet 2 to an armature shaft 3 of an electrical machine.
  • the ring magnet 2 is used for
  • the armature shaft 3 is also arranged in a stator (not shown) and is mounted in the stator housing by means of bearings. For reasons of a simplified illustration, only one bearing 10 is shown in FIG.
  • a fastening element 30 or tensioning element - also called a tensioning or clamping sleeve - is used to fasten the ring magnet 2 on the armature shaft 3.
  • the tensioning element 30 is designed such that it clamps on the armature shaft 3 and secures the ring magnet 2 against relative rotation and axial displacement relative to the armature shaft 3.
  • the tensioning element 30 is preferably made of spring steel, but should at least consist of a stiff but flexible material.
  • the fastening element 30 comprises a flange area 6, which is similar to that of FIGS. 2 and 3.
  • the flange region 6 is followed by a preferably sleeve-shaped intermediate section 32, to which its end section 34 adjoins, which preferably - similar to the previous embodiments - corresponds to a component fixedly arranged on the armature shaft 3.
  • the flange region 6 lies approximately in one plane and is preferably essentially in the form of a disk ring. This saves axial installation space. At the flange area 6 are acting in the direction of the end portion 34
  • the spring elements 7 are preferably also used for axial length compensation, which, due to the different temperature expansions of the material of the ring magnet 2 and the material of the armature shaft 3 or of the fastening element 30 are.
  • the spring elements 7 have the shape of ring disk segments which extend over approximately 90 °.
  • the spring elements 7 are connected to the intermediate section 32 via a radially extending connecting section 7a. With a middle section 7b, which is preferably essentially flat, the spring elements run at a distance around the intermediate section 32.
  • the connecting sections 7a and middle sections 7b run in a plane perpendicular to the longitudinal axis of the fastening element 30, but they can also protrude from this plane depending on the desired strength of the spring action.
  • the ends 7c of the spring element 7 are curved in the direction of the end section 34, the edges 7d pointing away from the end section 34.
  • the spring elements 7 with their center pieces 7b can also protrude radially and partially, for example
  • the intermediate section 32 first serves to connect the end section 34 and the fastening element 30 and can therefore has a geometrical design that serves this function and is adapted to the shape of the armature shaft 3; for example, this can be done by means of webs between the flange region 6 and the end section 34. Furthermore, the ring magnet 2 is arranged around the intermediate section 32, which further saves axial installation space, in particular compared to the previous exemplary embodiments.
  • the intermediate section 32 is preferably in the
  • Essentially cylindrical or has the shape of a cylindrical sleeve, as can be seen particularly clearly from FIG.
  • Inwardly directed projections (beads) or so-called spring pockets are also formed, which are provided as spring elements 8 in order to provide a spring or pretensioning force in the radial direction.
  • This design is particularly advantageous with regard to different thermal expansions of the intermediate section 32 and the armature shaft 3, since only a small radial installation space is required for this. This can be achieved by a snug fit.
  • a completely cylindrical intermediate section is also conceivable, on which a further elastic element or a so-called tolerance ring is arranged.
  • the spring elements 8 it is also possible for the spring elements 8 to be designed as radially extending, inwardly directed projections. However, the manufacture of the spring elements 8 shown, which run in the axial direction, is generally simpler.
  • the end section 34 adjoining the intermediate section 32 has at least one support area 36 for the ring magnet 2.
  • At least one of the armature shaft 3 at least obliquely protruding tab 38 for the ring magnet 2 to be provided.
  • a tab 38 is sufficient if the ring magnet 2 is secured radially by contact with the intermediate section 32. It is also conceivable that the tab 38 protrudes radially vertically. However, as shown, it is also possible to provide several tabs 38 on the circumference.
  • the tab or tabs 38 protrude obliquely outwards from the intermediate section 32 or lie on a conical one
  • the first end face S ⁇ of the ring magnet 2 has a conical inner region 40 which bears on the tabs 38.
  • a gap is provided between the ring magnet 2 and the intermediate section 34. This is achieved by dimensioning the
  • the ring magnet 2 may only come into contact with the intermediate section 34 at low operating temperatures. If the ring magnet 2 is in contact with the intermediate section 32 and the operating temperatures are not reached, the ring magnet 2 contracts more than the armature shaft 3 and the ring magnet 2 can tear open.
  • the spring elements 8 could also be omitted. Because with a different temperature expansion of the armature shaft 3 and the ring magnet 30, a correspondingly dimensioned gap is sufficient in the radial direction, whereby the spring elements 7 serve to compensate for different thermal expansions. In addition, the ring magnet 2 can even move on the tabs 38 or a region 36 which is adapted in accordance with the conical inner region 40.
  • the flange region 6 also preferably has protruding sections which serve to prevent rotation.
  • the sections for example so-called form ein ⁇ Hirtvertechnikung that ein ⁇ s corresponds to the surface of the end faces S Q _, S 2 of the annular magnet 2 and the fixture.
  • a resilient effect can also be achieved here by the tabs 40 in connection with adjoining spring elements 42. As a result, the ring magnet 2 is secured by frictional engagement, which is quite sufficient at low loads.
  • the spring elements 42 which connect to the tabs 40 and are distributed around the circumference of the end section 34, are supported on the armature shaft 3 and serve to prevent rotation and / or axial securing. At least one spring element 42 would be sufficient. With several spring elements 42, however, a more secure hold is guaranteed. It is also possible that the spring elements 42 are provided instead or additionally on the flange area 6 or another suitable location. In the exemplary embodiment shown, the lash-shaped spring elements 42 stand obliquely inwards.
  • the fastening arrangement according to FIGS. 14 and 15 serves to fasten the ring magnet 2 on the armature shaft 3 of an electrical machine.
  • the ring magnet 2 is used to determine the armature shaft speed and / or the armature shaft rotation direction.
  • the ring magnet 2 rests on the first end face S x on the end section 9 arranged fixedly or stationary on the armature shaft 3 and on the second end face S 2 on the flange region 6 of the fastening element 30.
  • the fastening element 30 provides a prestressing force in particular through the flange region 6 ready in the axial direction A and radial direction R of the armature shaft 3 or of the fastening element 30.
  • end section 34 which is fixedly arranged on the anchor wall, is part of the fastening element 30 or is integrated therein, and the end section 34 and the fastening member 30 are connected to one another via an intermediate section 34, around which the ring magnet 2 is arranged.
  • fastening element 30 can also be used to fasten ring-shaped components other than only that of ring magnets 3.
  • the present invention relates to a fastening arrangement
  • the fastening element 4, 14 provides a pretensioning force in the axial direction A and in the radial direction R in order to enable length compensation of heat-related changes in length and to secure against relative rotation between the armature shaft 3 and the ring magnet 2.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Permanent Field Magnets Of Synchronous Machinery (AREA)

Abstract

La présente invention concerne un dispositif de fixation permettant la fixation d'un aimant torique (2) sur un arbre d'induit (3) d'une machine électrique. Selon l'invention, l'aimant torique (2) est utilisé pour déterminer la vitesse de rotation de l'arbre d'induit et/ou la direction de rotation de l'arbre d'induit. Une première face (S1) de l'aimant torique (2) est en contact avec un composant (9) fixé sur l'arbre d'induit (3). Une seconde face (S2) de l'aimant torique (2) est en contact avec un élément de fixation disposé sur l'arbre d'induit (3). L'élément de fixation (4, 14, 30) est à l'origine d'une force de précontrainte agissant en direction axiale (A) et en direction radiale (R) pour compenser les variations de longueurs dues à la chaleur.
EP02782718A 2002-02-09 2002-10-14 Dispositif pour fixer un aimant torique sur un arbre d'induit Withdrawn EP1476936A1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10205412 2002-02-09
DE10205412 2002-02-09
DE10212507A DE10212507A1 (de) 2002-02-09 2002-03-21 Anordnung zur Befestigung eines Ringmagneten auf einer Ankerwelle
DE10212507 2002-03-21
PCT/DE2002/003877 WO2003067742A1 (fr) 2002-02-09 2002-10-14 Dispositif pour fixer un aimant torique sur un arbre d'induit

Publications (1)

Publication Number Publication Date
EP1476936A1 true EP1476936A1 (fr) 2004-11-17

Family

ID=27735662

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02782718A Withdrawn EP1476936A1 (fr) 2002-02-09 2002-10-14 Dispositif pour fixer un aimant torique sur un arbre d'induit

Country Status (3)

Country Link
EP (1) EP1476936A1 (fr)
HU (1) HUP0501194A2 (fr)
WO (1) WO2003067742A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004017716A1 (de) * 2004-04-10 2005-10-20 Bosch Gmbh Robert Rotor einer elektrischen Maschine
CN109003757B (zh) * 2018-08-07 2023-09-12 重庆科技学院 一种复合绝缘子的压接结构

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2061308T3 (es) * 1992-12-08 1994-12-01 Siemens Ag Accionamiento por motor electrico.
DE9315586U1 (de) * 1993-07-30 1993-12-09 Siemens Ag Elektromotorischer Antrieb
DE19546595A1 (de) * 1995-12-13 1997-06-19 Siemens Ag Drehzahl- und/oder Drehrichtung-Sensorvorrichtung
JP3517350B2 (ja) * 1998-03-18 2004-04-12 アスモ株式会社 モータ
DE19945657C1 (de) * 1999-09-23 2001-03-15 Siemens Ag Kommutatormotor mit einer Drehzahl- und/oder Drehrichtungs-Sensorvorrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO03067742A1 *

Also Published As

Publication number Publication date
HUP0501194A2 (en) 2006-04-28
WO2003067742A1 (fr) 2003-08-14

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