PERMANENT MAGNET ROTORS, ESPECIALLY FOR DYNAMO-ELECTRIC MACHINES

Abstract: A permanent magnet rotor (10) comprises a hub (12), to the periphery of which are attached, as by brazing, a number of wedge-shaped magnet support members (14). Between each adjacent pair of support members (14), there are mounted one or more permanent magnets (22), which are also wedge-shaped, with an angle of taper of, typically, 12 to 16 degrees. When rotating, the rotor is subjected to centrifugal forces which wedge the magnets (22) more firmly into the spaces between the support members (14), so that the magnets cannot escape, and will not be subjected to tensile stresses.

Description: "PERMANENT MAGNET ROTORS, ESPECIALLY FOR DYNAMO-ELECTRIC MACHINES" This invention relates to permanent magnet rotors, especially for dynamo-electric machines, such as alternators, synchronous a,c. motors, and also for magnetic couplings. The prior art U.S Patent No. 3,083,311 discloses an arrangement in which a permanent magnet rotor is used in an alternator. This rotor has a hub of a ferromagnetic material, around which are arranged a plurality of permanent magnets. Each of these magnets is somewhat wedge-shaped, with the narrower end of the wedge pointing radially outwards. The magnets are held in place by being embedded in a ring of aluminium which is @est in situ around the magnets and the hub. Thus, sen each adjacent pair of magnets, there is a wedgeshapes kart of the aluminium ring, and these wedgeshaped parts hold the magnets in place against centrifugal forces by their integral connection to the parts of the aluminium ring which lie axially beyond the ends of the magnets, and which in effect form two aluminium -d rings. Although the aluminium is in contact with the material of the hub, there will be little bond strength asisting the end rings in resisting centri fugal force. Such a structure is not suited to @@@ @rly @ od operation; in the specific exemple quoten in this prior U. S. patent, the rotor runs at 3600 r. p. m. Other rotor structures employing permanent magnets are disclosed in U. S. Patent No. 3,072,813 and German ratent Application No. 2,659,650. The German patent application discloses the use of ferrite magnets, which are often brittle and weak in tensile strength. then brittle magnets are used on a rotor, it has been conventional to surround them by a reinforcing hoop, which receives the centrifugal forces exerted on the magnets, so that The magnets are stressed in compression rather than in tension. In any structure which employs a ring or hoop to resist centrifugal forces, the radial thickness of the ring has to be increased as the design speed of the rotor is increased; as the speed increases, more and ore of the strength of the ring is used to withstand the bursting centrifugal forces exerted on the mass of the ring itself, and less and less strength is available to restrain the magnets against centrifugal forces. also, where the ring or hoop actually surrounds the magnets, there may be some difficulties in distributing tb centrifugal forces evenly over the contact area between magnet and hoop. Uneven distribution of these forces both stresses the hoop in bending, and may also result in cracking of the magnets. The use of a radially thick ring surrounding the magnets also results in increased reluctance of the magnetic circuit, and irerezsed flux leakage. Su @@arv of the invention A@cording to one aspect of the present invention, a permanent magnet rotor, which comprises a hub, a plurality of wedge-shape support members mounted around the perlphery of the hub, with their narrower ends adjacent the periphery of the hub, each of the spaces between adjacent support members also being wedgeshaped, but with its narrower end radially outwards, and a plurality of permanent magnets each received in one of the spaces between adjacent support members, each permanent magnet being wedge-shaped to match its space, is characterised in that each of the wedgeshaped support members is restrained against centrifugal forces by being attached by its narrower end to the hub, while each of the spaces between adjacent support members is open at at least one of its axially-facing limits, to allow insertion of the respective permanent magnet in an axial direction. with such a design of rotor, the wedge-shaped support members are better able to resist centrifugal forces than if they were merely supported at their ends by connection to end rings. Because the magnets need not be instrted until the assembly of hub and support nembers is cc: lete, the characteristics of the magnets do not imtese any limitation on the means used to connect the support members to the hub. In the preferred embodiment, the angle of taper of the permanent magnets and of the spaces within which the magnets are received is sufficiently small that the magnets are wedged in place by centrifugal forces, but not so small thet the magnets are erushed by the weiging action produced by centrifugal forces. This angle of taper may be beton on 4 and 18 degrees, preferably betwcen 12 and 16 degrees. As 2 further precHutic,n against fracture of magnets of relatively brittle material, a cushioning member may be interposed between each of the permanent magnets and each of the adjacent support members. These cushioning brs would be designed to distribute evenly over each magnet the compressive forces resulting from the wedging action of the magnet trying to move radially outwards. According to a second aspect of the invention, a rotor according to the first aspect is manufactured by 2 method which involves inserting the permanent magnets in an axial direction into the respective spaces between the support members, rotating the rotor at its maximum speed to wedge the magnets in place, and then machining the exterior surface of the rotor. The accompanying drawings illustrate various specific ttbodiments of the invention. Brief description of the drawings Figure 1 is z cross-section through part of a first design of permanent magnet rotor embodying the invention; Figures 2, 3 and 4 are views, similar to Figure 1, showing three further designs of rotor embodying the invention; Figure 5 is an elevation of one of a number of cushions incorporated in the rotor of Figure 4; Figure 6 is a section through the cushion, taken on the line VI-VI of Figure 5; and Figure 7 is a section, similar to Figure 6, through a second form of cushion which can be used in the rotor of Figure 4. Detailed description of the preferred embodiments Ref erring no to Figure 1, the first design of permanent magnet rotor for a dyr"s"'.o-electric machine is shown at 10, and ineludes a cylindricel hub 12, around which ere c-ff'xe twelve magnet support members 14 (three only shown in Figure 1). The hub 12 is made of a non-magnetic material, while the magnet support members 14 are made of a ferromagnetic material. The joint between the hub 12 and one of the magnet support merbers 14 is sh at 16; 2 variety of methods can be use@ to join the hub 12 and the support members 14, for era@ple: furnace brazing the two materials together; using 2 @ast bonding technlaue; diffusion bonding; or bonding by the hot isostatic pressure (HIP) process. oh of the magnet support members 14 is wedge shaped in section, as can be seen from Figure 1, with the narrower end of the wedge attached to the hub 12. The angle of taper of each support member 14 is such that the spaces 20 between adjacent support members are also wedge-shaped, as seen in section in Figure 1, but with the narrower end of the wedge radially outermost. A plurality of correspondingly wedge-shaped permanent magnets 22 are received in each of the spaces 20. The radially innermost surface of each magnet 22 in this example has slightly rounded corners 26 and 28, to ease insertion of the magnets 22 into the spaces 20. The Qimenslon of each magnet 22 in the radial direction is less than the radial depth of the spaces 20, so that a gap 24 is left between the radially innermost surfaces of the magnets and the adjacent surface of the space 20. This gap 24 does not constitute an interruption n the magnetic circuit of the machine, because the m2g -ts 22 are magnetised in the circumferential direction, so that the magnetic flux passes directly from the .Ebnets to the magnet support members 14, which act as pone pieces. As Figure 1 shows, alternate magnets 22 around the rotor 10 are magnetised in opposite directions. A thin hoop 30 which is heat shrink upon the @eripheral surface of the rotor 10 functions as an elsetric damper to intercept and diminish the flux variations caused by the fact that the stator surface of the dynamo-electric chin is riot smooth, but has teeth which cause a ripple in the flux, tending to produce eddy currents in the rotor 10. The hoop 30 helps to prevent these flux variations from penetrating into the support members 14 and into the magnets 22, by virtue of the fact that opposing eddy currents are produced in the hoop 30, thereby shielding the permanent magnets 22 and the support members 14. The hoop 30 consists of a high strength, non-magnetic material preferably having a low resistivity, such as a beryllium copper alloy. The process of assembling the rotor 10 involves first sliding the magnets into the space 20, and then rotating the rotor 10 at its maximum allowable speed. At this stage, the hoop 30 has not yet been fitted. During rotation the magnets 22 move radially outwards owing to centrifugal force. The angle of taper of the we5gc'-shaped spaces 20 is so chosen that the magnets 22 are corseouently wedged in place in the spaces 20, even after the rotor 10 has ceased rotating. The outer surfaces of the support members 14 and the magnets 22 Ere then ground to the proper dimensions and the hoop 50 is shrunk ono the rotor periphery, thus completing the asseDly. The angle of taper of the spaces 20 is critical. Half this angle, that is to say, the angle formed between the wall of the spaces 20 and a plane passing through the axis of the rotor 10 arid through the centre of the magnet 22 should be slightly less than the angle of friction. This r.r & lc s exper2mentally determined and is the maximum angle at which a locking wedge action is achieved for the material and conditions pertinent to a given design. If the angle of taper is too large the magnets 22 will not remain locked in place after the rotor ceases to rotate and if the angle is too small, lateral crushing forces nay cause the magnet to fracture. Therefore, there is a critical range within which the locking angle e must lie. It has been found that the size of the locking angle 6 should usually be between 2 to 9 degrees, preferably f to 8 degrees. Although the wedging action of the magnets 22 within the spaces 20 is primarily responsible for resisting the centrifugal forces on the magnets 22, the hoop 30 also provides a small restraining force on the magnets. The support members 14 each have through holes 18 disposed near the periphery of the rotor 10, for reducing the mass of the support members 14, so that the rotor 10 can operate at high speed. The holes 18 are circular in the rotor of Figure 1; in general, this is the easiest shape of hole to produce. As well as lightening the support embers 14, the holes 18 allow c f'o.' of coolr:.g air through the rotor, which helps to dissipate any heating resulting from eddy currents. S"rlarly, cooling air can flow through the gaps 24 at the innermost ends of the magnets 22. A further function of the gap 24 is to provide a stress relieving radius at the 'oot of the support rs 14. The roter ch@wn in Figure 2 is generally similar to that shown in Figure 1, and the same reference numbers will be uced for corresponding parts. The primary difference between the two rotors is that, in the rotor of Figure 2, the lightening and cooling holes 18 are not circular in section, but are elongated in the radial direction. Holes of this shape are somewhat more difficult to produce, but result in lighter weight, and a higher permissible speed for the rotor 10. The centripetal acceleration to which the parts of the rotor are subjected is proportional to the distance from the rotor axis, so that the most benefit, in terms of reducing the stress on critical sections (such as the joint 16) is obtained by removing mass from the support members 14 at as great a radius as possible. Figure 3 shows a further rotor; again, the same reference numbers will be used for corresponding parts. The magnets 22 in Figure 3 are radially magnetised, while the hub 12 consists of a ferromagnetic material and the support members 14 consist of a non-magnetic material. In such an arrangement, each gap 24 would ioirrl an interruption in the magnetic circuit, and therefor the t zs 24 are each filled with a closure shim 32 of a ferromagnetic or a permanent magnet material to reduce substantially the reluctance which the gap 24 would otherwise create. The shims 32 are inserted into the gaps 24 after the magnets 22 have locked in place as described above. The rotor 10 of Fig@re 3 also has dampening bers jlr whi oh are losate near the rotor's periphery and extend through the support rbers 14; the ends of the bers 34 are interconnected by end rings (not shown). When used with the dampening hoop 30 the bars 34 provide aided electrical dampening. Alternatively, the 1-rs 34 cn be used without the hoop 30 to intercept ann diminish the flux harmonics caused by the stator. The rotor 10 shown in Figure 4 is generally simila ar to that shown in Figure 3, but includes, on each side of each magnet 22, between the magnet 22 and the adjacent magnet support member 14, a ferromagnetic cushioning member 30 The purpose of the cushioning members 30 is to help to distribute tangential crushing forces evenly over the magnets 22, and thereby help to prevent fracture of the magnets 22, which may often be of a relatively brittle material. Figures 4 and 5 show one of the cushioning members 33 in grater detail. The member 50 has a smooth side 32 and an embossed or patterned side 34, t which in this example bears an array of short cylindrical protrusions. he nbossed side 34 of the cushion 30 is preferably in contact with the support member 14. The smooth side 32 f the cushion 30 preferably fits flush against the magnet 22 so that no gap in the flux path exists between the cushion 30 and the magnet 22. The purpose of the e.: embossed side 34 cf the cushion 30 is to provide room for the material of the cushion 30 to yield or flow locally and thus avoid any excessive localized @@ or pressure between the support member 14 and @@ magnet 22, which could otherwise exist, going to manufacturing toler @s or to deformations of the support members 14 and/or deformations of the @ @s 22 with changing temperature or speed. The embossed side 34 also allows the cushion 30 to conform to the shape of the space between the support member 14 and the magnet 22. The embossed pattern is designed to provide a low bulk modulus and to provide spaces so that the material can flow locally where stresses are high because of manufacturing inaccuracies or distortion caused by the high operating speeds. The embossed pattern permjits greater freedom in selecting the optimum cushion material for transmission of magnetic flux without saturation. The mechanical properties can be achieved by adjusting the hole pattern area to achieve an effective yield stress tnat exceeds the average stress required to support the magnet loads at speed but is below the yield stress of the magnet material. One possible material for the cushioning member 30 is a nickel alloy. Non-magnetic materials such as aluminium, or glass fibres in an epoxy resin matrix, can be used for the cushion where low yield strength and @@ material flow is required. Of course, cushioning members can also be incorporated in rotors of the types shown in Figures 1 and 2. In these rotors, the cushioning members would not form part of the magnetic circuit, and therefore the magnetic properties of the cushioning members are not @ nt in these c@@. In another embodiment, @@ in Figure @, a multiple layer cushion 40 is used to project the relatively fragile @ @s 22 from fracturing at high speeds. A first layer @ of the cushion 40 has an embossed surface and a smooth surface, while a second layer 44 has two smooth surfaces. The embossed surface of the layer should be placed adjacent to the support members 14.

Claims: CLAIMS 1. A permanent magnet rotor, which comprises a hub, a plurality of wedge-shaped support members mounted around the periphery of the hub, with their narrower ends adjacent the periphery of the hub, each of the spaces between adjacent support members also being wedgeshaped, but with its narrower end radially outwards, and a plurality of permanent magnets each received in one of the spaces between adjacent support members, @@ permanent magnet being wedge-shaped to match its spare, characterised in that each of the wedge-shaped support members (14) is restrained against centrifugal forces by being attached Dy its narrower end to the hub (12), while each of the spaces between adjacent support members (IA) is osen at at least one of its axially-facing limits, to allow insertion of the sitive permanent magnet (22) in axial direction. 2. A rotor as claimed in Claim 1, which each of the permanent magnets (22) is of 2 relatively brittle material. @ A rot or a 5 r r or Claim 2 in @ of the support @ (14) has a lightening hole (18). 4. A rotor is @@ im Claim 3, in which each lightening hole (18) has a cross-section which is elongated in the radial direction. 5. A rotor as claimed in any of the preceding claims, which has, around the support members (14) and the magnets (22), a hoop (36) of a strong material with high electrical conductivity. 6. h rotor as claimed in any of the preceding claims, in which the angle of taper of the permanent magnets (22) and of the spaces within which the magnets are received is sufficiently small that the magnets are wedged in place by centrifugal forces, but not so small that the magnets are crushed by the wedging action produced by centrifugal forces. 7. A rotor as claimed in Claim 6, in wnich the said angle of taper is between 4 and 18 degrees, preferably between 12 and 16 degrees. 8. A rotor as claimed in any of the preceding claims, in which a cushioning member (30) is interpose between each of the permanent magnets (22) and each of the adjacent support members (14). 9. A rotor claimed in Cleim 8 in which each cushioning member (30) has a snooth face (32) and an opp@@ei face having feetures (34) which reduce the @r of the cushioning member which contacts en adjacent member. 10. A rotor as claimed in Claim 8 or Claim 9, in which each cushioning member (30) is made of either nickel alloy, aluminium, or glass fibres in an epoxy resin matrix. 11. A rotor as claimed in Claim 8 or Claim 9 or Calm 10, in which each cushioning member (30) is made of a ferromagnetic material having a compressive yield strenght less than the compressive yield strenght of the material of the permanent magnets (22). 12. k method of manufacturing a rotor as claimed in any of the preceding claims, in which the permanent magnets (22) are inserted in an axial direction into ne r respective SOCS between the support members (14), the rotor is the related at its maximum speed to wedge the magnets (22) in place, and the exterior surface of the rotor is then machined.

Inventors: BURGMEIER, LYMAN R., MC'CARTY, FREDERICK B., SILVER, ALEXANDER
Applicants: THE GARRETT CORPORATION
Application year: 1979
Main classification: H02K1
IPC codes: H02K1