EP3646439A1 - Rotor for an electrical machine - Google Patents
Rotor for an electrical machineInfo
- Publication number
- EP3646439A1 EP3646439A1 EP18732321.7A EP18732321A EP3646439A1 EP 3646439 A1 EP3646439 A1 EP 3646439A1 EP 18732321 A EP18732321 A EP 18732321A EP 3646439 A1 EP3646439 A1 EP 3646439A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotor
- shaft
- spring element
- rotor magnet
- magnet assembly
- 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.)
- Pending
Links
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/28—Means for mounting or fastening rotating magnetic parts on to, or to, the rotor structures
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/22—Rotating parts of the magnetic circuit
- H02K1/27—Rotor cores with permanent magnets
- H02K1/2706—Inner rotors
Definitions
- the invention relates to a rotor for an electric machine and an electric machine with such a rotor.
- a ring magnet can be glued to the shaft. This is the standard procedure for neodymium-iron-drilling magnet magnets because they are very brittle.
- an adhesive must cure, and an uneven adhesive distribution can lead to an imbalance of the rotor.
- curing takes a set time, and assembly lines where an electric machine is completed every two to four seconds require very long assembly lines because of the curing time.
- a corresponding rotor can be mounted quickly and no gluing or screwing is required.
- the components can be easily formed, and this allows a slight imbalance of the rotor.
- the spring element makes it possible to compensate for different coefficients of expansion of the materials used, which lead to different lengths at different temperatures.
- the ring member allows the transmission of torque from the connection assembly to the shaft.
- the rotor has a second fastening arrangement, which is adapted to a movement of
- Rotor magnet arrangement to limit in at least one axial direction. This allows a resilient clamping connection of the rotor magnet assembly and thus a torque transmission from the rotor magnet assembly to the shaft via a frictional connection with axial pressure.
- the second fastening arrangement has a spring element and a ring element and is arranged at least in sections around the shaft.
- the ring element is fixed to the shaft by means of a press-fit connection and limits movement of the spring element in at least one axial direction.
- the spring element is designed to prevent movement of the
- Rotor magnet assembly to limit in the axial direction. This allows holding the rotor magnet assembly via two spring elements of one each
- the rotor magnet arrangement is at least partially between the first mounting arrangement and the second
- the mounting arrangements can therefore be axially spaced from each other, and this facilitates assembly.
- the rotor magnet assembly has a clearance fit on the shaft. The risk of excessive mechanical stresses between the rotor magnet assembly and the shaft is thereby reduced compared to a press-fit connection, but it is still possible radial guidance.
- the shaft is in the range of
- Rotor magnet arrangement formed circular cylindrical. Such waves can be made very accurately and are suitable for high speeds.
- the press-fit connection between the ring element and the shaft is provided in a predetermined first axial region, which axial axial region of the rotor magnet assembly is spaced. This reduces the risk of a negative effect of the press-fit connection on the area of the rotor magnet arrangement.
- the shaft is formed in the region of the ring member is cylindrical with a circular or polygonal cross-section.
- Such a wave can be made very accurately and has good balancing properties.
- the ring element is formed as a hollow cylinder with a circular or polygonal cross-section. This facilitates the joining with the shaft and it can also be used cylindrical waves.
- the ring element has teeth directed towards the shaft, which teeth cooperate with the shaft to form the press-fit connection.
- the strength of the press-fit connection and the joining force can be influenced as desired by the size and shape of the teeth.
- the spring element is at least partially elastically deformed. This elastic deformation leads to a higher force and thus to a better connection.
- the spring element is designed as a plate spring.
- Disc springs can transmit forces well, and they can be well calculated.
- Rotor magnet assembly are connected to each other with a frictional connection to a torque transmission between the rotor assembly and the
- Rotor magnet arrangement and can also be used for very brittle magnets.
- the spring element is designed to allow a contact with an end face of the rotor magnet arrangement. This allows via the clamping action a force in the axial direction, in the radial direction and in the circumferential direction.
- the rotor magnet arrangement has a jacket surface, and the spring element is designed to allow contact with the jacket surface. This allows both a backup of
- Rotor magnet arrangement can be achieved in the circumferential direction and in the axial direction and in the radial direction.
- the spring element and the rotor magnet arrangement on positive-locking elements, which together a
- the spring element has slots which divide the spring element into segments which are at least partially decoupled from each other in their spring action.
- Ring element firmly connected to each other or integrally formed.
- the one-piece design facilitates the joining of the rotor, since fewer components are present.
- Ring element formed in several parts. For the production of the elements, this leads to a simplification.
- the ring element is designed as a collar on the spring element. This design facilitates the handling of the fastening arrangement, since the ring element is arranged on the spring element.
- Mounting arrangement formed non-ferromagnetic. That reduces one
- Mounting arrangement formed of a material containing chromium and nickel. Such a material is good for a press-fit connection and for a
- Fastening arrangement formed as a deep-drawn part or as a rotating part. This production has proven to be advantageous for connection to the shaft.
- Rotor magnet assembly exclusively on the at least one
- Rotor magnet arrangement an inner surface and the shaft on an outer surface adjacent to this inner surface, wherein a maximum of 20% of the inner surface of the recess is in contact with the outer surface of the shaft, more preferably at most 10% and more preferably at most 5%. This reduces the risk of damage due to mechanical stress between the components.
- the rotor magnet assembly and the shaft are not in direct contact.
- stresses are avoided, which can occur, for example, at different thermal expansion coefficients.
- a corresponding direct connection is not required, as the Rotor magnet assembly via the mounting assembly is indirectly connected to the shaft.
- a hollow-cylindrical cavity is provided between the rotor magnet arrangement and the shaft.
- the rotor magnet assembly contains neodymium, iron and boron. Magnets with neodymium-iron-boron alloys are particularly strong but also very brittle. Therefore, they are usually attached by gluing. The resilient clamp connection has proven to be a good alternative.
- no adhesive bond is provided between the rotor magnet assembly and the shaft.
- Adhesive bonds are the standard process for many types of magnets, but they require drying time to produce, and the solvents commonly used are out
- the invention allows a connection without adhesive.
- the object is also achieved by an electric machine with a stator, a bearing arrangement and a rotatably mounted on the bearing assembly rotor.
- the rotor can be used advantageously.
- the bearing arrangement has at least one rolling bearing with an inner ring and an outer ring, wherein the inner ring rests against the ring element.
- the ring element can thus be used on at least one side as a spacer.
- FIG. 1 shows a shaft and a rotor magnet arrangement
- 2 shows in a longitudinal section the shaft and magnet arrangement of FIG. 1 with a first fastening arrangement
- Fig. 3 in a longitudinal section a rotor with the shaft, rotor magnet assembly and first mounting arrangement of Fig. 2 and a second
- Fig. 5 is a plan view of an embodiment of the rotor with teeth on the
- FIG. 6 is a plan view of an embodiment of the rotor with a shaft having a polygonal cross-section
- FIG. 7 is a plan view of an embodiment of the rotor with slots in the first connection arrangement
- FIG. 8 shows a longitudinal section through the embodiment of the rotor of FIG. 3 with a schematic representation of the deformation of the spring element, FIG.
- FIG. 9 shows in a longitudinal section a further embodiment of the rotor with a multi-part first connection arrangement
- Fig. 10 in a longitudinal section an embodiment of the rotor with
- FIG. 13 is a longitudinal section of an embodiment of the rotor
- Fig. 14 in a longitudinal section an embodiment of the rotor
- FIG. 15 shows an electric machine with the rotor of FIG. 2.
- Fig. 1 shows a shaft 22 and a rotor magnet assembly 30, which is to be added to the rotor shaft 22.
- the rotor shaft 22 has a first shaft end 221 and a second shaft end 222.
- the shaft ends 221, 222 preferably each have a phase 223, 224 to a
- the rotor magnet arrangement 30 has a first end face 31, a second end face 32, a lateral surface 33 and a recess 34.
- the recess 34 serves to enable the rotor magnet arrangement 30 to be pushed onto the shaft 22.
- Rotor magnet arrangement 30 has, by way of example, four rotor poles 301, 302, 303, 304, but other pole numbers are also possible, for example 2, 6, 8, etc.
- the rotor magnet arrangement 30 can be produced, for example, from a permanent magnetic material, it can also be produced from a plastic with embedded magnetic particles, or a plurality of individual magnets can be fastened to a carrier component. In the production of one
- a permanent magnetic material for example, a production via sintering or sawing from a magnetic material is possible.
- a permanent magnetic material may be used which contains neodymium, iron and boron. Neodymium iron boron alloys are magnetically very strong
- the neodymium-iron-boron alloy is preferably added further elements.
- other rare earth elements such as dysprosium and erbium increase the temperature stability of the magnetization, and cobalt can be added to increase the corrosion resistance.
- the shaft 22 is preferably circular-cylindrical in the area of the rotor magnet arrangement 30, since such a shaft 22 can be produced easily and with high accuracy. However, it is also possible a polygonal cross section or another cross section. After pushing the rotor magnet assembly 30 on the shaft 22, this is already performed relative to the shaft 22. For a complete attachment of the
- Rotor magnet arrangement must be considered as remaining degrees of freedom in particular axial forces and a relative torque occurring during acceleration between the rotor magnet assembly 30 and the shaft 22.
- Fig. 2 shows in a longitudinal section the shaft 22 which extends through the recess 34 of the rotor magnet assembly 30 therethrough.
- Attachment assembly 41 attached to the shaft 22.
- the fastening arrangement 41 has a spring element 51 and a ring element 52 and is arranged at least in sections around the shaft 22.
- the ring member 52 has an inner surface 521 defining a recess 522 and is fixed to the shaft 22 by a press-fit connection 226.
- a press-fit connection there is a press fit or interference fit between the shaft 22 and the rotor magnet arrangement 30, ie the dimension of the shaft 22 in the region of the press fit is at least partially greater than the corresponding dimension of the recess 522 before the components are joined.
- the inner surface 521 is formed at least partially hollow cylindrical with a circular cross section, but it can also be a polygonal
- the shaft 22 is preferably also formed in the region of the ring member 52 is cylindrical with a circular or polygonal cross-section.
- the spring element 51 is designed in the manner of a plate spring.
- the spring element 51 preferably has the shell shape of a truncated cone.
- the shape of the spring element 51 may also be referred to as disk-shaped.
- the spring member 51 is internally connected to the ring member 52, and formed integrally therewith, and externally, it may contact the rotor magnet assembly 30 in contact. If the
- Rotor magnet assembly 30 is moved towards the mounting assembly 41, the spring element 51 springs in and becomes flatter.
- the spring element 51 can thus limit a movement of the rotor magnet arrangement 30 in the first axial direction 241.
- the rotor magnet assembly 30 preferably has a clearance fit 227 on the shaft 22. Permanent magnet materials often have brittle material properties and therefore should preferably not be exposed to extreme stresses.
- Tolerances for the clearance fit on the shaft are preferably narrowly specified in one embodiment.
- the rotor magnet arrangement 30 may be provided with a transition fit or an interference fit.
- the spring element 51 and the ring element 52 are integrally formed. But it can also be provided a fixed connection between the separated before the joining spring element 51 and ring member 52.
- the ring element 52 is formed in the embodiment as a collar on the spring element 51.
- FIG. 3 shows in a longitudinal section the rotor 20, wherein, in contrast to FIG. 2, a second fastening arrangement 42 is additionally provided, which is designed to limit a movement of the rotor magnet arrangement 30 at least in the second axial direction 242.
- the second fastening arrangement 42 is constructed in the embodiment in the same way as the first fastening arrangement 41, and the embodiments in Fig. 2 apply accordingly.
- the spring element 51 may be a movement of the
- the rotor magnet arrangement 30 is arranged at least in sections between the first fastening arrangement 41 and the second fastening arrangement 42. This enables a good assembly, in which the first fastening arrangement 41 and the second fastening arrangement 42 can be pushed onto the shaft 22 from different sides. Sections of the rotor magnet assembly 30 may overlap axially with portions of the mounting assembly 41 and 42, respectively. By clamping the rotor magnet assembly 30 between the
- Rotor magnet assembly 30 This allows a torque transmission between the rotor assembly 30 and the spring member 51.
- the spring member 51 In addition, the
- Embodiment very small spring travel and thus a compact design of the rotor 20.
- the mounting assembly 41 is still in the relaxed state, since the rotor magnet assembly is not yet acted upon with a force to the left.
- the mounting assembly 41 is spring-loaded.
- Rotor magnet assemblies 30 with neodymium, iron and boron are brittle and are therefore usually glued. Experiments have shown that attachment of neodymium-iron-boron magnets via the mounting assemblies 41, 42 works well and allows very high speeds without destroying the rotor magnet assembly 30.
- FIG. 4 shows the rotor 20 with a first bearing 81 and a second bearing 82, wherein the first fastening arrangement 41, the rotor magnet arrangement 30 and the second fastening arrangement 42 are arranged between the two bearings 81, 82.
- the bearings 81, 82 are formed as rolling bearings, and they each have an inner ring 83 and an outer ring 84.
- the inner ring 83 is at least at one of the bearings 81, 82 against the associated mounting assembly 41, 42 at.
- the bearings 81, 82 may additionally be provided a spring between this and the mounting arrangement to form a floating bearing.
- the inner ring 83 may be one or both
- Mounting arrangements 41, 42 are arranged on the ring member 52, and this allows a very compact design in the axial direction.
- the ring element 52 is preferably formed at least partially cylindrical on the lateral surface in order to push the inner ring 83 well.
- a bearing 81, 82 can of course be used other types of bearings such as plain bearings.
- FIG 5 shows a plan view of the rotor 20 with a further embodiment of the first fastening arrangement 41.
- a plurality of teeth 53 are provided on the inner surface 521 of the ring member 52 so as to form the press-fit connection 226 with the shaft 22.
- the teeth 53 may also be provided in a plurality of axially spaced-apart planes.
- FIG. 6 shows a plan view of a further embodiment of the rotor 20 with the first fastening arrangement 41, wherein both the shaft 22 and the inner surface 521 have a polygonal cross-section.
- the cross section is hexagonal, but it may, for example, also be formed pentagonal or with a different number of corners. Mixed forms are also possible in which the inner surface 521 is polygonal and the shaft 22 is circular, or vice versa.
- FIG. 7 shows a plan view of a further embodiment of the rotor 20.
- a plurality of slots 54 are provided on the spring element 51.
- the spring element 51 is divided into a plurality of segments 51 A, 51 B, 51 C, 51 D, which are at least partially decoupled from each other in their spring action. This allows
- Bumps on the front side of the rotor magnet assembly 30 are better balanced, and there is a softer spring behavior.
- Fig. 8 shows a longitudinal section of a fragmentary embodiment of the rotor 20.
- the first connection assembly 41 is mounted on the shaft 22, and the
- Rotor magnet assembly 30 is pressed against the spring member 51.
- Clarification of the spring action is the unpressed form of the spring element 51 with 51 ', and the embedded form with 51. It can be seen how the spring element 51 through the rotor magnet assembly 30 to the first shaft end 221 out is deformed.
- the deformation of the spring element 51 is preferably at least
- the spring element 51 has on the rotor magnet assembly 30 side facing in the radially outer region compressive stress and in the radially inner region of the tensile stress.
- This embodiment enables a simple configuration of the spring element 51, since it can be connected directly to the ring element 52 in the radially inner region and comes into contact externally with the rotor magnet arrangement 30, which enables good torque transmission.
- the spring element 51 may for example be formed such that it extends from the ring element 52 in a first portion radially outward and then extends radially inwardly in a second portion. In this case, the spring member 51 radially inwardly enters the rotor magnet assembly 30 in contact.
- this embodiment is less well suited to a torque transmission between the
- the first fastening arrangement 41 is formed in two parts or generally in several parts, the ring element 52 abutting against the spring element 51 at a point 55, so that a further displacement of the radially inner region of the Spring element 51 is prevented in the axial direction 241.
- the spring element 51 can thus spring in the direction 241 during a movement of the rotor magnet arrangement 30.
- the spring element 51 is in contact with the lateral surface 33 of FIG.
- Connection arrangement 41 allows.
- the spring element 51 and the rotor magnet arrangement 30 have positive-locking elements 51 1, 305, which together form an anti-twist device for the transmission of torque.
- Spring element 51 has a pin or hook 51 1, and the rotor magnet assembly a matching recess 305. These elements can also be arranged reversed, or both components 30, 51 may have pins that act together. On the other hand, such a spring element 41 can also absorb forces in the axial direction 242, and with a fixed connection between the spring element 51 and the ring element 52, a configuration without a second spring element 42 is possible. The absorption of forces in both axial directions 241, 242 is also possible via other types of connection, for example via a screw, the
- FIG. 10 shows an embodiment of the rotor 20 in which the spring element 51 and the rotor magnet arrangement 30 have positive-locking elements 51 1, 305, which together provide an anti-rotation lock between the spring element 51 and the rotor
- Rotor magnet assembly 30 form for the transmission of torque.
- the spring element 51 has a pin 51 1, and the rotor magnet assembly has a matching recess for this, so that the pin 51 1 can engage in the recess.
- the spring element 51 may have a recess and the rotor magnet arrangement 30 may have a pin.
- FIG. 11 shows the rotor 20 with a spring element 51, which is indeed designed as a plate spring, wherein it is flatter in the radially inner region than in the radially outer region.
- the spring element has figuratively speaking a kink, with this kink disappearing more and more, the stronger the plate spring is tensioned.
- FIG. 12 shows the rotor 20 with a first fastening arrangement 41, which has the spring element 51 and ring element 52.
- the second mounting arrangement 42 has a simpler structure and is designed as a rod, which is inserted through a recess in the shaft and limits a movement of the rotor magnet arrangement 30 in the axial direction 242.
- the spring action is achieved in this embodiment only by the spring element 51 of the first fastening arrangement 41.
- Fig. 13 shows the rotor 20, which is formed by the basic structure as the rotor 20 of Fig. 3.
- the rotor magnet assembly 30 is spaced from the shaft 22.
- the recess 34 of the rotor magnet assembly 30 is thus larger than the shaft 22, and there remains a gap 35 between the shaft 22 and the rotor magnet assembly 30.
- the rotor magnet assembly 30 is thus held by the mounting assemblies 41, 42 both in the axial and in the radial direction, without the shaft 22 in direct contact with the
- Rotor magnet assembly 30 occurs.
- This embodiment can be assembled by aligning the rotor magnet assembly 30 with the assembly relative to the shaft. After mounting the
- Embodiments are also possible in which the rotor magnet assembly 30 is largely spaced from the shaft 22, but in a few places has contact.
- the shaft 22 has an adjacent to the inside of the recess 34 surface. Quantitatively, it is advantageous if this is a maximum of 20% of this
- FIG. 14 shows another embodiment of the rotor 20.
- the press-fit connection 226 between the ring element 52 and the shaft 22 is provided in a predetermined first axial region 523.
- This first axial region 523 is of the
- Rotor magnet assembly 30 axially spaced.
- the ring element 52 and the spring element 51 are connected to each other by a connecting element 56, wherein the connecting element 56 is at least partially spaced from the shaft 22.
- the embodiment shown is advantageous because the ring element 52 is usually at least partially plastically deformed in the region of the press-fit connection 226. If the ring element 52 and the spring element 51 directly adjoin one another, this can also lead to a plastic deformation in the region of the spring element 51. This does not have to be critical for the spring action of the spring element, but it makes the calculation or design of the spring element more difficult. In the In contrast to the embodiment of FIG. 14, the spring element 51 and the ring element 52 are largely unaffected or decoupled from one another, and the calculation of the spring element 51 and the ring element 52 is quite possible.
- Fig. 15 shows schematically an electric machine 10 with the rotor 20. Die
- Electric machine 10 may be designed as a motor or as a generator.
- Electric machine 10 has a housing 12, a stator 14 with a stator core 16 and a winding arrangement 18.
- the winding arrangement 18 is connected to a control device 15 for activation.
- the rotor 20 is rotatably supported via the first bearing 81 and the second bearing 82.
- the bearings 8, 82 form a bearing arrangement 81, 82.
- An application 19 is fastened to at least one end of the shaft 22, for example a fan wheel, a toothed wheel or a drive wheel of a generator.
- the at least one fastening arrangement 41, 42 is preferably formed from a non-ferromagnetic material, more preferably from a non-magnetic or non-magnetic material.
- Useful flow is not influenced by the fastening arrangement 41, 42.
- a material which contains chromium and nickel has proved to be positive. But it is also another material possible, for example, a metal, a metal alloy, a
- Plastic or a plastic composite Plastic or a plastic composite.
- a preparation of the first or second fastening arrangement 41, 42 as a deep-drawn part or as a rotating part is advantageously possible and allows a favorable mass production.
- the training as a deep-drawn part is advantageous due to the geometrically simple shape. Assembly of the rotor
- the shaft 22 is fixed, and the first attachment assembly 41 is pressed from the first shaft end 221 to a predetermined position on the shaft. Subsequently, the
- Fastening assembly 42 from the second shaft end 222 of pressed onto the shaft 22, see. Fig. 3. Either the second fastening assembly 42 can be pressed to a predetermined position on the shaft 42, or it can during
- Rotor magnet assembly 30 between the two mounting arrangements 41, 42 is sufficiently clamped. If the rotor magnet arrangement 30 has flat end faces, there is no need to align the components in the circumferential direction, and this facilitates assembly.
- Rotor magnet arrangement 30 are preferably formed without adhesive. Basically, a joining of the spring element 51 and the ring element 52 by a
- the assembly of the bearing assembly 81, 82 can be done in the usual way, for example by sliding the bearings 81, 82 on the shaft.
- the rotor 20 may be formed without the second attachment assembly 42. For this purpose, however, it is necessary that the first fastening arrangement 41 the
- Movement of the rotor magnet assembly 30 limited in both axial directions. This can be achieved, for example, by connecting the first fastening arrangement 41 to the rotor magnet arrangement 30, for example by means of a positive connection, or that the first fastening assembly 41 is bonded to the rotor magnet assembly 30.
- the rotor magnet assembly 30 has a cylindrical shell in the embodiments. It is also possible to use rotor magnet arrangements 30 with other geometries, for example with elliptical, angular or flattened ones
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102017114720.9A DE102017114720A1 (en) | 2017-06-30 | 2017-06-30 | Rotor for an electric machine |
PCT/EP2018/065993 WO2019001992A1 (en) | 2017-06-30 | 2018-06-15 | Rotor for an electrical machine |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3646439A1 true EP3646439A1 (en) | 2020-05-06 |
Family
ID=62683211
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18732321.7A Pending EP3646439A1 (en) | 2017-06-30 | 2018-06-15 | Rotor for an electrical machine |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP3646439A1 (en) |
CN (1) | CN211151651U (en) |
DE (2) | DE102017114720A1 (en) |
WO (1) | WO2019001992A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA3134252A1 (en) * | 2019-03-19 | 2020-09-24 | Magna International Inc. | High performance electromagnetic machine and cooling system |
US11177703B2 (en) * | 2019-08-08 | 2021-11-16 | Garrett Transportation I Inc | Rotor assembly for permanent magnet electric motor with radially biasing shaft structure |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2952483A (en) * | 1954-12-27 | 1960-09-13 | Licentia Gmbh | Means for holding a stack of laminations for use in electric machines and the like apparatus |
US3082338A (en) * | 1961-03-06 | 1963-03-19 | Vincent K Smith | Rotor assembly for dynamoelectric machine |
US6177749B1 (en) * | 1998-11-12 | 2001-01-23 | Emerson Electric Co. | Polygonal shaft hole rotor |
DE10331958A1 (en) * | 2003-02-26 | 2004-09-09 | Robert Bosch Gmbh | Electric machine, e.g. electronically commutated DC motor, has permanent magnet elastically mounted on rotor by holding members |
JP2009112158A (en) * | 2007-10-31 | 2009-05-21 | Aisan Ind Co Ltd | Rotor and pump |
DE102011076159A1 (en) * | 2011-05-20 | 2012-11-22 | Robert Bosch Gmbh | Electric machine with an axial spring element |
JP5685506B2 (en) * | 2011-08-19 | 2015-03-18 | 株式会社安川電機 | Rotating electric machine rotor, rotating electric machine and rotor end face member |
DE102011088362A1 (en) * | 2011-12-13 | 2013-06-13 | Robert Bosch Gmbh | Holding element for permanent magnets on a rotor of an electric machine |
-
2017
- 2017-06-30 DE DE102017114720.9A patent/DE102017114720A1/en active Pending
-
2018
- 2018-06-15 CN CN201890000911.6U patent/CN211151651U/en active Active
- 2018-06-15 EP EP18732321.7A patent/EP3646439A1/en active Pending
- 2018-06-15 DE DE212018000250.9U patent/DE212018000250U1/en active Active
- 2018-06-15 WO PCT/EP2018/065993 patent/WO2019001992A1/en active Application Filing
Also Published As
Publication number | Publication date |
---|---|
WO2019001992A1 (en) | 2019-01-03 |
CN211151651U (en) | 2020-07-31 |
DE102017114720A1 (en) | 2019-01-03 |
DE212018000250U1 (en) | 2020-05-08 |
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