• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention relates to mechanical engineering, in particular to contactless electromagnetic supports. The purpose of the invention is increased durability and reduced manufacturing costs. This goal is achieved by the fact that axial-radial channels for supplying a coolant are made in the stop ferromagnetic ring. On the outer cylindrical surface of the thrust ring can be fixed axial blades, ensuring the movement of the coolant in the axial direction. In all cases, the rotating thrust ring of the magnetic bearing functions as the impeller of the fan and provides effective cooling of both the ring itself and the electromagnets interacting with it, as well as the circulation of the cooling medium throughout the device, for example, the electric drive. 9. з the item f-ly 8 ill. (Ls
    公开号:SU1734579A3
    申请号:SU884356829
    申请日:1988-11-17
    公开日:1992-05-15
    发明作者:Гласс Дитер；Айксельбергер Вильфрид；Бюрер Петер
    申请人:Асеа Браун Бовери Аг (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to mechanical engineering, namely to contactless electromagnetic supports for suspending rotating bodies.
    The purpose of the invention is to increase service life and reduce manufacturing costs.
    FIG. 1 shows half of a magnetic bearing; cross section: FIG. 2 is a section A-A in FIG. 1, in FIG. 3 shows an embodiment of channels in the form of drilled holes; in fig. 4 - half of the magnetic bearing with blades, the cross section; in fig. 5 - installation of the bearing in the housing of the electric drive; in fig. 6 is a partial section a bb nz FIG. five; in fig. 7 — node I in FIG. five; in fig. 8 is a view of BB in FIG. 7
    The bearing assembly contains electromagnets 1 and 2, p; displaced on both sides of the ferrocompacting digging tool 3. The ring 3 is provided with several channels 4, which are mainly passing from the horizontal direction. These channels are evenly distributed and extend from the section of the adapter sleeve 5 to the outer cylindrical edge 6 the stop ring 3 and end with the outlet 7. Thus, the flow of gaseous coolant can be directed from the portion of the adapter sleeve 5 to the outer edge 6 of the stop ring 3. The channels 4 pass through rub the thrust ring 3 and divide it into the main ring 8 and an additional protective ring 9, and on the protective ring 9 there is a left thrust surface 10, on the main ring 8 - the right thrust surface 11 Ring 3 is installed on the wall 12.
    FIG. 2 shows the course of the channels 4 inside the stop ring 3 The channels 4 in the peripheral direction are bounded by radial blades 13, which in the direction 14 of the rotation of the stop ring 3 are bent by vj
    CJ
     ate
    4 S

    WITH
    ass In the direction of the axis of the shaft 12, the channels 4 are bounded by the main 8 and the protective 9 rings. The channels 4 are axially tapered from the portion of the adapter sleeve 5 to the outer edge 6. The outlet 7 of the channels 4 is in the center between the two abutment surfaces 10 and 11.
    The main 8 and protective 9 rings, as well as connecting both rings 8 and 9, the radial vanes 13 are expediently made integral, i.e. casting For small bearings, it is more advisable to carry out the main 8 and protective 9 rings, as well as the radial blades 13 as separate parts and connect them into the stop ring by soldering, welding or riveting.
    FIG. 3, the channels 15 have parts 16 and 17, respectively. Part 16 consists of a series of radial-opening holes that are arranged vertically with respect to the axis of the shaft 12 and are evenly distributed around the perimeter. The holes of the first part 16 start from the cylindrical outer edge 6 of the stop ring 3 and end at the portion of the adapter sleeve 5. The hole portion 5 is provided in the section of the adapter sleeve 5 extending from the side of the stop ring 3 left in the drawing in the direction of the shaft axis 12. These holes form the second part of the channel 15, therefore, each of these axial holes passes to the radial hole, forming the first part 16 of the channel 15.
    FIG. Figure 4 shows a thrust magnetic bearing, carrying the cooling substance in the axial direction with axial vanes 18. Axial vanes 18 are mounted on a cylindrical outer edge 19 of the anvil ring 3, which in this case has no channels. An outer rim 19 is provided with a circumferential annular groove 20 in which the bases of the 21 axial blades are fixed with screws or rivets 22. A number of axial vanes 18, which form a blade crown, are evenly distributed around the perimeter of the anvil ring.
    FIG. 5 shows an electric drive with a motor shaft 23 running vertically. The actuator 24 is equipped with a thrust magnetic bearing, but the magnetic bearing has two electromagnets that act on one thrust surface.
    The motor 24 has a closed case, fixed by a flange 25 on the wall 26 of the structural unit, in particular a blower or compressor, by means of screws 27. The shaft 23 of the engine is directed through the opening 28 in
    the construction site and on it are installed the blades of the blower or compressor. A first bearing shield 29 is provided on the flange portion 25 on the engine housing, which is made in the form of a disk and extends approximately perpendicular to the vertical axis 30 of the engine shaft. In the center of the first bearing shield 29, two ball horn 31s are fixed, which stabilize the motor shaft 23 in the radial direction. At the same time, there is a slide fit between the ball bearings 31 and the bearing shield, so the motor shaft can
    5 to move freely in the axial direction (the direction of the vertical axis 30). To seal the inner space 32 of the electric motor, seals are mounted in the area of the ball bearings 31.
    On the opposite end of the first bearing shield, according to the drawing, the end of the electric motor 24 has a second bearing shield 33 in the form of a disk, also
    5 extending approximately perpendicularly relative to the vertical axis 30. The lower shaft end of the engine shaft is supported radially on the center of this second bearing shield 33 by means of a ball bearing 34 fixed to it. By appropriately fitting the bearing, the engine shaft can move slightly in the axial direction. Uch5 drain ball bearing 34 is closed relative to the surrounding space using the outer cover 35 of the bearing. The second bearing shield 33 is mounted on an approximately annular cylindrical bearing housing 36, which is an integral part of the motor housing. For this purpose, the bearing housing is fixed by means of an annular flange 37 by means of screws on the ring 5 of the cylindrical part 38 of the electric motor housing, in which a package 40 of the stator core of the electric motor together with the electric winding is fixed with two ring disks 39. The disks 39 are fixed perpendicularly relative to the vertical axis 30 in the housing part 38 and the stator core package is located between them. Between the stator core package 40 and the housing part 38 is formed a ring cavity 41, connected through a series of holes 42 located in the disks 39, with the internal space 32 of the electric motor. Inside the package 40 of the stator core, the rotor 43 of the electric motor is mounted on the shaft 23.
    A bearing housing 36 with a clearance relative to the second bearing shield 33 is provided with a first circular support ring 44 which runs approximately perpendicular to the vertical axis 30 and surrounds the motor shaft 23 with a sufficient clearance. With an axial clearance relative to the first bearing ring 44, the second bearing ring 45 is also provided in the bearing housing 36, which is designed and installed similarly to the first bearing ring 44. On the facing surfaces of the bearing rings 44 and 45 located perpendicularly on the vertical axis 30, is fixed on electromagnet 1 and 2 thrust magnetic bearing. Each of the electromagnets has an electric coil. In the annular intermediate space between the electromagnets 1 and 2 placed thrust ring 3 of the magnetic bearing. The stop ring 3 is mounted on the shaft 23 of the electric motor and is made the same. as in FIG. one.
    FIG. 6, the cylindrical outer edge 6 of the retaining ring 3. And hence the area where the outlets 7 of the radial channels 4 are located, passes with a small gap relative to the annular inner wall 46 of the bearing housing 36. The radial vanes 47 are bent backwards with respect to the direction 14 of rotation.
    An annular groove 51 is provided in the annular cylindrical wall 48 of the bearing housing 36 opposite the outlet openings 49 of the channels 50, the axial width of which, preferably remaining constant, is equal to the axial width of the outlet openings 49. The annular groove 51 is coaxially arranged during operation, and the coolant flowing out of the channels 52 easily flows into the annular groove 51.
    A radially outer portion of the annular groove 51 is evenly distributed over a series of forwardly bent stationary guide vanes 53, which block the annular opening in the radial direction and ensure the integrity of the housing 36. On the radial inner portion 54 of the annular groove, the guide vanes are not provided. The radial length of the sections 50 and 54 is approximately the same. To ensure that the annular groove 51 is sufficiently long in the radial direction, the bearing housing 36 is provided on the outside with an annular flange 55, into which the annular groove 51 is extended.
    A winding of cooling pipes 56 is installed outside the housing part 38, while the cooling pipes are provided with outer radial ribs 57. FIG.
    5 shows only a few turns of the cooling tubes. The ends of the cooling tube are connected to the connecting lines 58. Between the end of the winding of the cooling tubes and the flange 25 in the annular cylindrical part 38 of the housing, a number of radial holes 59, preferably drilled from the outside into the inner space 32 of the electric motor 24, are evenly distributed.
    5 of the cooling tubes is surrounded by an annular cylindrical jacket 60 adjacent to the ribs 57. The end of the jacket 60 closest to the bearing housing 36 is open and forms an annular inlet opening 61 for the coolant. The opposite end of the jacket 60 is tightly connected to the housing part 38 in such a way that the holes 59 are inside the jacket and extend into the annular cavity 62 formed between the handle 5 and the housing part 38.
    The motor 24 is not in contact with the surrounding air, it is installed in a sealed cavity or surrounded
    0 with a gap in the sealed enclosure 63. Connecting lines 58 extend through the housing 63 to the outside.
    FIG. Figure 7 shows node I as a separate part and as an embodiment. The stop ring 3 is made in the same way as in FIG. 4. The retaining ring has a crown of axial vanes 18, ending with a small gap in front of the cylindrical inner wall of the housing 38, continued in this
    In case of the same diameter up to the second bearing shield 33, which is fixed on the housing part 38, a second row evenly distributed around the perimeter is provided in the second bearing shield 33
    5 holes 64. through which the gaseous coolant can exit the inner space 32 of the electric motor. The gap between the axial blades 18 and the cylindrical inner wall of the case 38 is 1-3 mm.
    The upper support ring 45, as well as the lower support ring 44, on which the electromagnets of the thrust magnetic bearing are located, on the axial section
    The 5 blades are provided with a series of uniformly distributed holes 65 or 66 along the perimeter.
    Through the bore 65, the coolant during engine operation comes from the inside
    32 electric motors to the axial blades 18 and from them through the bore holes 66 located in the lower support ring and the hole 64 is led outside.
    In order to minimize the loss of gaseous coolant flow, the passage openings 65 and 66 are provided with guide vanes 67 or 68 extending axially to a portion of the axial blades 18. The guide vanes are integrated into a blade crown.
    FIG. 8 shows fixed guide vanes 67 and 68, between which rotating axial blades 18 are mounted. Axial blades 18 and guide vanes 67 and 68 are respectively evenly distributed around the perimeter.
    Thrust magnetic bearing works as follows.
    During operation, the electric current passes through the coils of electromagnets 1 and 2. As a result, ne resistant surfaces 10 and 11 exert magnetic forces. which hold the stop ring 3 in a suspended state, therefore the magnetic bearing can sense the axial forces of the shaft without contact of the stop surfaces 10 and 11 with electromagnets 1 and 2 during rotation of the stop ring 3.
    The heat generated by electromagnets 1 and 2 is transferred by radiation and convection to the thrust surfaces 10 and 11, therefore, the thrust ring of the bearing 3 is also heated. Additionally, the bearing ring 3 is heated by eddy currents and aerodynamic friction. As the shaft rotates, the gaseous coolant is sucked into the channels 4 and directed to the outer edge 6 of the ring 3, where it exits the holes 7.
    In this case, the thrust ring 3 is cooled.
    Axial blade 18 during rotation of the stop ring provide the movement of the cooling means E in the axial direction (parallel to the axis of the shaft 12). Coolant is supplied to both electromagnets 1 and 2 (Fig. 7). Heat from the electromagnets 1 and 2 is removed by means of the blades 67 and 68, and the axis of the stop ring 3 is removed by the blades 18.
    During operation of the electric motor 24, the ball bearings 31 and 34 radially center the vertical shaft 23 of the engine, while the stop ring 3, in conjunction with the electromagnets 1 and 2, through which the electric current flows, performs the function of an axial stop of the engine shaft. The axial emphasis perceives the axial forces acting in the direction of the vertical axis 30 on the motor shaft 23. These forces are made up of the weight of the rotating parts and axial forces caused by the machine connected to the engine shaft 23. At the same time, the stop ring 3, using the channels 4 provided for in it, sucks the gaseous cooling substance, preferably air, nitrogen or helium,
    0 located in the inner space, from the inner space 32 of the electric motor and feeds it through the annular opening 51 into the cavity between the electric motor 24 and the housing 63. From here and the cooling substance flows through the annular cavity 62 between the jacket 60 and the housing part 38 to the openings 59 and enters into the inner space of 32 electric motors. During the course of
    0 of the annular cavity 62, the gaseous cooling substance is in contact with the cooling pipes 56 and their fins 57 and gives off heat to the cooling water or coolant flowing through the cooling pipes.
    5 Supply and discharge of cooling water or refrigerant through the connecting lines 58 occurs in such a way that the heat exchange takes place in countercurrent. Gaseous coolant
    0, during its flow from the holes 59 to the stop ring 3, it perceives the heat loss of the electric motor, and when passing through the stop rings 52 of the stop ring, the heat loss of the magnetic bearing is also perceived. These heat losses are then released through cooling pipes 56 to the cooling water or refrigerant, and then removed from the system.
    If the motor 24 is directly exposed to ambient air, i.e. case 63 is absent, it is advisable to exclude the cooling coil 56 and the jacket 60. From the annular opening 51, the heated cooling substance, which in this case consists of air, goes into the surrounding space, and from the surrounding space into the internal space 32 enters perceives loss
    0 heat the motor and the magnetic bearing and takes them into the surrounding space.
    The axial thickness of the stop ring in the area of the stop surfaces 10 and 11 of co5 places approximately 0.5-1.0 shaft diameters on which the stop ring is attached. The axial width of the radial channels in the area of the outer edge of the stop ring is approximately 0.2-0.7 times the thickness of the stop ring in this area. The number of radial and guide vanes is approximately 8-30 pcs. The maximum thickness of the working and guide vanes is approximately 0.2-0.4 times the thickness of the stop ring in the area of the stop surfaces. The radial length of the axial blades is approximately 0.1-0.3 times the diameter of the stop ring. The number of axial blades is chosen in such a way as to ensure a sufficient supply of coolant, the number of guide vanes must match the number of axial blades.
    By using this thrust magnetic bearing, it is efficiently cooled using simple means and at the same time other heat-generating structural units, groups or aggregates can be cooled using a coolant flow that is set by the thrust ring. Therefore, no other means of supplying gaseous coolant is required.
    权利要求:
    Claims (10)
    [1]
    1. A bearing assembly comprising at least one electromagnet, a shaft with a central adapter sleeve secured thereto, equipped with an axial ferromagnetic ring with at least one anvil surface for interacting with at least one electromagnet differing in that. what. In order to increase service life and reduce manufacturing costs, in the thrust ring, in the main direction, channels for supplying a gaseous coolant flowing from the adapter sleeve to the periphery of the thrust ring are provided.
    [2]
    2. Node under item 1, characterized in that. that the ferromagnetic stop ring consists of a circular primary and additional circular protective rings defining the channels in the axial direction, and radial blades placed between the said rings and limiting the channels in the radial direction, each ring having a stop surface for an electromagnet.
    [3]
    3. Node according to claim 2, characterized in that the radial blades are curved from the center
    rings to its periphery in the direction opposite to the direction of rotation.
    [4]
    4. A unit according to claim 1, characterized in that the channels are formed from two orthogonal portions, preferably made in the form of drilled holes, in the axial and radial directions, respectively.
    [5]
    5. Node on PP. 1-4 with a drive, in particular, an electric motor, characterized in that the bearing is mounted in the inner cavity of the drive; in the housing of the drive, an annular groove of an annular thrust ring with guide vanes arranged substantially radially arranged therein is provided.
    [6]
    6. The knot of claim 5, wherein the bend of the guide vanes is opposite to the bend of the radial blades.
    [7]
    7. An assembly comprising at least one electromagnet, a central shaft adapter sleeve, equipped with an axial ferromagnetic ring with at least one anvil surface for interacting with at least one electromagnet, characterized in that, in order to increase service life and reduce costs for manufacturing, working axial vanes are installed on the thrust ring for supplying gaseous cooling substance in the axial direction.
    [8]
    8. The knot according to claim 7, characterized in that the axial blades are made straight and preferably fixed evenly
    on the outer cylindrical surface of the thrust ring.
    [9]
    9. Node on PP. 7 and 8, with a drive, in particular an electric motor, characterized in that the bearing is mounted in
    the internal cavity of the actuator, the axial blades are located in the radial direction with a small gap relative to the internal surface of the drive housing, the bearing is equipped
    support rings for mounting electromagnets on them, while the rings are made with through holes for supplying gaseous coolant and are installed in front of and behind the axial blades
    in the direction of flow of the coolant.
    [10]
    10. A unit according to claim 9, characterized in that the through holes are provided with guide vanes.
    6 7
    //
    2
    FIG. 1 A - A
    /
    FIG. 2
    FIG 3
    26
    I I
    3532 DA
    FIG. five
    FIG. four
    28 7
    5fcKfcSS
     JT s / / - ± i
    25
    33 I
    45.
    Fig 7
    6-6
    50
    Fie.6
    6-in
    65
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    同族专利:
    公开号 | 公开日
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE3740295A|DE3740295C2|1987-11-27|1987-11-27|
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