A passive magnetic bearing structure with radial vibration suppression

Abstract

The application discloses a kind of active and passive magnetic bearing structure with radial vibration suppression effect, it is related to magnetic suspension bearing technical field, including: annular stator magnetic conductor, it is equipped with annular cavity in it, and its ring hole inner wall is equipped with annular opening;Rotor assembly, rotor assembly includes rotor shaft and thrust disc;Rotor shaft is arranged in stator magnetic conductor ring hole;Thrust disc is sleeved on the outer periphery of rotor shaft and its outer periphery side is active and penetrates annular opening;Axial control coil, axial control coil is coaxially nested in annular cavity;Stator permanent magnet one and rotor permanent magnet one;Stator permanent magnet one is coaxially fixed at one end of stator magnetic conductor, to form magnetic field at annular opening;Rotor permanent magnet one is sleeved on rotor shaft and corresponds stator permanent magnet one, both are axially magnetized and opposite polarity magnetic pole;Conductor vibration suppression disc, conductor vibration suppression disc is located between rotor permanent magnet one and stator permanent magnet one.The application can effectively suppress the radial vibration of rotor and has small volume, high operating stability.

Description

Technical Field

[0001] This invention relates to the field of magnetic levitation bearing technology, and in particular to a dynamic and passive magnetic bearing structure with radial vibration damping effect. Background Technology

[0002] Magnetic levitation bearings utilize magnetic force to suspend a rotor in an air gap. They offer advantages such as frictionless operation, oil-free operation, high speed, and active control, making them suitable for high-precision, high-vacuum, and ultra-clean applications. Magnetic levitation bearings can be categorized into active and passive types based on the method of magnetic force delivery. Active magnetic bearings utilize electromagnets, feedback control loops, sensors, and power amplifiers to achieve active control of the bearing force. Passive magnetic bearings, on the other hand, derive their bearing force solely from the permanent magnet itself. Active magnetic bearings can achieve extremely low rotor vibrations through high-precision control algorithms; however, their closed-loop feedback control system, composed of sensors, controllers, and power amplifiers, is bulky, power-consuming, and costly. Passive magnetic bearings, with their simple structure, require no control system, consume no energy, and offer high reliability. However, their inherently low damping means they cannot effectively suppress rotor vibrations when supported components undergo displacement, impacting system reliability. Currently, a common approach is to add an active control coil to a passive magnetic bearing, but this requires a corresponding control board and sensors, significantly increasing system cost, size, and complexity, while reducing reliability. Hybrid active and passive magnetic bearings can combine the characteristics of the two types of magnetic bearings mentioned above, giving full play to the advantages of active magnetic bearings such as high control precision, low vibration, and high stability, while reducing the loss and size of active magnetic bearings. However, existing active and passive magnetic bearing systems generally only integrate the two types of magnetic bearings in physical space, still requiring a lot of electromagnetic components, making it impossible to simplify the control structure, resulting in difficulty in miniaturization, low equipment applicability, and poor radial vibration suppression effect.

[0003] Therefore, how to propose a passive magnetic bearing structure with radial vibration suppression function, which can automatically and effectively suppress the rotor when radial vibration occurs, thereby reducing the rotor vibration amplitude, and has the characteristics of small size and high operational stability, is a problem that urgently needs to be solved by those skilled in the art. Summary of the Invention

[0004] In view of this, the present invention proposes a dynamic and passive magnetic bearing structure with radial vibration damping effect, aiming to solve the technical problems of large volume, poor radial vibration damping effect and low operation stability of the above-mentioned traditional dynamic and passive hybrid magnetic bearings.

[0005] To achieve the above objectives, the present invention adopts the following technical solution:

[0006] This invention provides a structure for an active and passive magnetic bearing with radial vibration damping effect, comprising:

[0007] A stator magnetic conductor, wherein the stator magnetic conductor is annular and has an annular cavity extending circumferentially inside; the inner wall of the annular hole of the stator magnetic conductor has an annular opening extending circumferentially and communicating with the annular cavity.

[0008] The rotor assembly includes a rotor shaft and a thrust disk; the rotor shaft is coaxially disposed in the annular hole of the stator magnetic conductor; the thrust disk is coaxially sleeved on the outer peripheral wall of the rotor shaft, and its outer peripheral side movably passes through the annular opening; both sides of the thrust disk have a preset axial active adjustment gap with the inner wall of the corresponding annular opening.

[0009] An axial control coil, coaxially nested within the annular cavity, is used to form an adjusting magnetic field between the opposing inner walls of the annular opening.

[0010] A stator permanent magnet and a rotor permanent magnet are provided. The stator permanent magnet is coaxially sleeved outside the rotor shaft and fixed to one end of the stator magnetic conductor to form magnetic fields in opposite directions at the inner wall surfaces of the annular opening. The rotor permanent magnet is coaxially sleeved on the rotor shaft and corresponds to the side of the stator permanent magnet away from the stator magnetic conductor. Both the rotor permanent magnet and the stator permanent magnet are axially magnetized with opposite magnetic poles facing each other to provide a radial passive restoring force for the rotor shaft.

[0011] A conductor vibration damping plate is coaxially sleeved on the rotor shaft and located between the rotor permanent magnet and the stator permanent magnet; a preset axial passive adjustment gap is provided between the conductor vibration damping plate and the stator permanent magnet.

[0012] This invention combines a stator permanent magnet I and a rotor permanent magnet I into a radial passive magnetic bearing structure. When the rotor shaft experiences radial displacement, the radial restoring force between the stator permanent magnet I and the rotor permanent magnet I returns the rotor shaft to its equilibrium position. When the rotor shaft experiences radial vibration, the stator permanent magnet I and the rotor permanent magnet I deviate radially, causing the magnetic flux acting on the conductor damping disk to alternate. This alternating magnetic flux induces eddy currents, resulting in eddy current losses, which convert vibration energy into heat loss and thus suppress radial vibration. The permanent magnet flux generated by the stator permanent magnet and rotor permanent magnet of the active-passive combined magnetic bearing structure of this invention forms a working magnetic flux at the preset axial active adjustment gap between the two sides of the thrust disk and the inner wall of the annular opening, providing bias magnetic flux for the axial magnetic bearing. When the rotor shaft undergoes axial displacement, the axial control coil forms an adjustment magnetic field between the relative inner walls of the annular opening through control current. The adjustment magnetic field generated by the axial control coil and the bias magnetic field generated by the stator permanent magnet and rotor permanent magnet are superimposed to change the strength of the magnetic field in the preset axial active adjustment gap, thereby generating an actively adjustable axial electromagnetic force to ensure the stability of the axial position of the rotor shaft.

[0013] As a further improvement to the above technical solution, there are multiple stator permanent magnets and multiple rotor permanent magnets; the multiple stator permanent magnets are arranged in a ring and concentrically radially spaced, and are all fixed at one end of the stator magnetic conductor; the multiple rotor permanent magnets are arranged in a ring and concentrically radially spaced, and are all mounted on the rotor shaft; the multiple rotor permanent magnets correspond one-to-one axially to the multiple stator permanent magnets; the conductor vibration damping disk corresponds between the multiple stator permanent magnets and the multiple rotor permanent magnets.

[0014] The beneficial effects of the above technical solution are: the axial arrangement of multiple concentric radially spaced stator permanent magnets and multiple concentric radially spaced rotor permanent magnets relative to each other can form greater stiffness and radial vibration suppression effect.

[0015] As a further improvement to the above technical solution, it also includes a magnetic focusing and magnetic isolation component, which includes a magnetic focusing ring and a magnetic isolation ring; the magnetic focusing ring is provided at the end of each of the plurality of rotor permanent magnets near the conductor damping disk; the magnetic isolation ring is provided between any two adjacent stator permanent magnets, between any two adjacent rotor permanent magnets, and between any two adjacent magnetic focusing rings.

[0016] The beneficial effects of the above technical solution are: the magnetic focusing ring plays the role of focusing permanent magnet flux and can improve passive stiffness and vibration damping effect; the non-magnetic magnetic isolation ring plays the role of separating adjacent magnetic focusing rings, adjacent stator permanent magnets and adjacent rotor permanent magnets, so as to further improve structural stiffness and stability.

[0017] As a further improvement to the above technical solution, the magnetic ring is made of a high magnetic permeability material.

[0018] The beneficial effects of the above technical solution are: the magnetic ring made of high magnetic permeability material can further concentrate the permanent magnet flux to penetrate the conductor vibration damping disk, thereby increasing the radial eddy current vibration damping effect while improving the passive stiffness.

[0019] As a further improvement to the above technical solution, it also includes a second stator permanent magnet and a second rotor permanent magnet; the second stator permanent magnet is coaxially sleeved outside the rotor shaft and fixed at the other end of the stator magnetic conductor; the second stator permanent magnet is coaxially sleeved on the rotor shaft and corresponds to the side of the second stator permanent magnet away from the stator magnetic conductor; both the second stator permanent magnet and the second rotor permanent magnet are axially magnetized and have opposite magnetic poles facing each other, so as to provide radial passive restoring force for the rotor shaft; the second stator permanent magnet and the first stator permanent magnet are arranged with the same magnetic poles facing each other along the axial direction of the stator magnetic conductor.

[0020] The beneficial effects of the above technical solution are: the combination of stator permanent magnet II and rotor permanent magnet II forms a radial passive magnetic bearing, forming a structure in which radial passive magnetic bearings are symmetrically arranged at both ends of the stator magnetic conductor, which further increases the stability of rotor shaft operation; the combination of stator permanent magnet II and stator permanent magnet I can make the magnetic field distribution in the preset axial active adjustment gap more balanced.

[0021] As a further improvement to the above technical solution, both the rotor shaft and the thrust disk are made of magnetically conductive material.

[0022] The beneficial effects of the above technical solution are: the rotor shaft and thrust disk made of magnetically conductive material can reduce the magnetic loss of the permanent magnet circuit formed by stator permanent magnet one and rotor permanent magnet one, as well as the permanent magnet circuit formed by stator permanent magnet two and rotor permanent magnet two, which is conducive to realizing the miniaturization of permanent magnet structure volume.

[0023] As a further improvement to the above technical solution, both the stator permanent magnet and the rotor permanent magnet are made of ferrite permanent magnet material or rare earth permanent magnet material.

[0024] As a further improvement to the above technical solution, the conductor vibration damping disk is made of a high conductivity material with a thickness of 1-2 mm.

[0025] The beneficial effects of the above technical solution are: when the rotor shaft experiences radial vibration, the conductor damping disk made of high conductivity material can generate a large eddy current in the conductor damping disk, thereby damping the radial vibration and achieving a stronger vibration suppression effect.

[0026] As a further improvement to the above technical solution, the axial control coil is made of copper wire with a diameter of 0.2mm-1mm.

[0027] As a further improvement to the above technical solution, the preset axial active adjustment gap is 0.1mm-1mm; the preset axial passive adjustment gap is 1mm-2mm.

[0028] As can be seen from the above technical solution, compared with the prior art, the present invention discloses a dynamic and passive magnetic bearing structure with radial vibration damping effect, which has the following advantages and beneficial effects:

[0029] 1. The active-passive combined magnetic bearing structure of the present invention realizes that the radial passive magnetic bearing and the axial active magnetic bearing share electromagnetic components, thereby enabling the miniaturization of the overall structure.

[0030] 2. The radial passive control and axial active control of the active-passive combined magnetic bearing structure of the present invention only require one coil and one control circuit, which greatly reduces power consumption.

[0031] 3. The active-passive combined magnetic bearing structure of the present invention integrates a passive radial vibration suppression element, thereby making the rotor shaft vibrate less and the operation more stable.

[0032] 4. The active-passive combined magnetic bearing structure of the present invention adopts an upper and lower double-set passive permanent magnet ring structure (stator permanent magnet one and rotor permanent magnet one form one set of permanent magnet rings, stator permanent magnet two and rotor permanent magnet two form another set of permanent magnet rings), which can realize the upper and lower mutual cancellation of the axial attraction of the radial passive part, thereby making the operation more stable. Attached Figure Description

[0033] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0034] Figure 1 A schematic axial cross-sectional view of an active and passive magnetic bearing structure with radial vibration damping function according to the present invention.

[0035] Figure 2 A schematic diagram of the permanent magnet circuit of the stator permanent magnet and the rotor permanent magnet of an active and passive magnetic bearing structure with radial vibration damping function according to the present invention.

[0036] Figure 3 A schematic diagram of the electromagnetic circuit generated by the axial control coil of an active-passive magnetic bearing structure with radial vibration damping effect according to the present invention;

[0037] Figure 4 A schematic diagram of the installation state of the stator permanent magnet II and the rotor permanent magnet II of an active and passive magnetic bearing structure with radial vibration damping function according to the present invention.

[0038] Figure 5 The present invention provides a schematic diagram of the permanent magnet circuits of stator permanent magnet one and rotor permanent magnet one, and the permanent magnet circuits of stator permanent magnet two and rotor permanent magnet two, which are active and passive magnetic bearing structures with radial vibration damping function.

[0039] Figure 6 A schematic diagram of the electromagnetic circuit generated by the axial control coil in a stator permanent magnet II and a rotor permanent magnet II configuration of an active and passive magnetic bearing structure with radial vibration damping function according to the present invention.

[0040] In the diagram: 1. Stator magnetic conductor; 11. Annular cavity; 12. Annular opening; 121. Preset axial active adjustment gap; 2. Rotor assembly; 21. Rotor shaft; 22. Thrust disk; 23. Magnetic guide ring; 3. Axial control coil; 4. Stator permanent magnet one; 5. Rotor permanent magnet one; 6. Conductor vibration damping disk; 61. Preset axial passive adjustment gap; 7. Magnetizing and insulating assembly; 71. Magnetizing ring; 72. Insulating ring; 8. Stator permanent magnet two; 9. Rotor permanent magnet two. Detailed Implementation

[0041] Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and intended to explain the present invention, and should not be construed as limiting the present invention.

[0042] In the description of this invention, it should be understood that the terms "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0043] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0044] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0045] According to embodiments of the present invention, such as Figure 1 As shown, a driven magnetic bearing structure with radial vibration damping function includes:

[0046] The stator magnetic conductor 1 is annular and has an annular cavity 11 extending circumferentially inside it; the inner wall of the annular hole of the stator magnetic conductor 1 has an annular opening 12 extending circumferentially and communicating with the annular cavity 11.

[0047] Rotor assembly 2 includes a rotor shaft 21 and a thrust disk 22. The rotor shaft 21 is coaxially disposed in the annular hole of the stator magnetic conductor 1. The thrust disk 22 is coaxially sleeved on the outer peripheral wall of the rotor shaft 21, and its outer peripheral side moves through the annular opening 12. There is a preset axial active adjustment gap 121 between the two sides of the thrust disk 22 and the inner wall of the corresponding annular opening 12.

[0048] Axial control coil 3 is coaxially nested in an annular cavity 11 to form an adjustment magnetic field between the relative inner walls of the annular opening 12.

[0049] Stator permanent magnet 4 and rotor permanent magnet 5; stator permanent magnet 4 is coaxially sleeved outside rotor shaft 21 and fixed to one end of stator magnetic conductor 1 to form magnetic fields in opposite directions at opposite inner wall surfaces of annular opening 12; rotor permanent magnet 5 is coaxially sleeved on rotor shaft 21 and corresponds to the side of stator permanent magnet 4 away from stator magnetic conductor 1; rotor permanent magnet 5 and stator permanent magnet 4 are both axially magnetized and opposite magnetic poles are opposite to each other to provide radial passive restoring force for rotor shaft 21;

[0050] The conductor vibration damping plate 6 is coaxially sleeved on the rotor shaft 21 and located between the rotor permanent magnet 5 and the stator permanent magnet 4; the conductor vibration damping plate 6 and the stator permanent magnet 4 have a preset axial passive adjustment gap 61.

[0051] In this embodiment, the combination of stator permanent magnet 4 and rotor permanent magnet 5, forming a combined active and passive magnetic bearing structure, constitutes a radial passive magnetic bearing. When the rotor shaft 21 experiences radial displacement, the radial restoring force between stator permanent magnet 4 and rotor permanent magnet 5 causes the rotor shaft 21 to return to its equilibrium position. When the rotor shaft 21 experiences radial vibration, stator permanent magnet 4 and rotor permanent magnet 5 deviate radially, causing the magnetic flux acting on the conductor damping disk 6 to alternate. The changing magnetic flux induces eddy currents, resulting in eddy current losses, which convert vibration energy into heat loss and thus suppress radial vibration. The permanent magnet flux generated by the stator permanent magnet 4 and rotor permanent magnet 5 of the active-passive combined magnetic bearing structure of this invention forms a working magnetic flux at the preset axial active adjustment gap 121 between the two sides of the thrust disk 22 and the inner wall of the annular opening 12, providing bias magnetic flux for the axial magnetic bearing. When the rotor shaft 21 undergoes axial displacement, the axial control coil 3 forms an adjustment magnetic field between the relative inner walls of the annular opening 12 through control current. The adjustment magnetic field generated by the axial control coil 3 and the bias magnetic field generated by the stator permanent magnet 4 and rotor permanent magnet 5 are superimposed to change the strength of the magnetic field in the preset axial active adjustment gap 121, thereby generating an actively adjustable axial electromagnetic force to ensure the stability of the axial position of the rotor shaft 21.

[0052] For details, see Figure 2 and Figure 3 The working principle of the active axial control of rotor shaft 21 is as follows: Assuming rotor shaft 21 is placed vertically, Figure 2 The solid line loop with the arrow represents the magnetic flux path generated by stator permanent magnet 4 and rotor permanent magnet 5. These paths produce magnetic fluxes in opposite directions in the air gaps on both sides of the thrust disk 22, which can be labeled φp. 上 ,φp 下 The magnetic flux path generated by the energized axial control coil 3 is as follows: Figure 3 As shown by the dashed loop with arrows, magnetic flux in the same direction is generated in the air gaps on both sides of the thrust disk 22, which can be labeled as φi. 上 ,φi 下 Therefore, the total magnetic flux in the air gaps on both sides of the thrust disk 22 is φp on the upper side. 上 +φi 上 The lower side is φp 下 -φi 下 Clearly, the magnetic flux on the upper side of the thrust plate 22 is higher than that on the lower side, thus generating an upward attractive force on the thrust plate 22. Similarly, when a reverse current flows through the axial control coil 3, it will generate a downward attractive force on the thrust plate 22. Therefore, by controlling the magnitude and direction of the current in the axial control coil 3, active axial control of the rotor shaft 21 can be achieved.

[0053] Specifically, the stator magnet 1 is made of a magnetic material, such as iron; for example, electrical pure iron or low carbon steel can be used.

[0054] In some embodiments, there are multiple stator permanent magnets 4 and multiple rotor permanent magnets 5; the multiple stator permanent magnets 4 are arranged in a ring and concentrically radially spaced, and are all fixed to one end of the stator magnetic conductor 1; the multiple rotor permanent magnets 5 are arranged in a ring and concentrically radially spaced, and are all mounted on the rotor shaft 21; the multiple rotor permanent magnets 5 axially correspond one-to-one with the multiple stator permanent magnets 4; the conductor damping disk 6 corresponds between the multiple stator permanent magnets 4 and the multiple rotor permanent magnets 5.

[0055] The stator permanent magnets 4 and rotor permanent magnets 5 arranged concentrically and radially spaced are positioned opposite each other in the axial direction to form greater stiffness and radial vibration suppression.

[0056] In some embodiments, the system further includes a magnetic focusing and magnetic isolation component 7, which includes a magnetic focusing ring 71 and a magnetic isolation ring 72; a magnetic focusing ring 71 is provided at the end of each of the multiple rotor permanent magnets 5 near the conductor damping disk 6; a magnetic isolation ring 72 is provided between any two adjacent stator permanent magnets 4, between any two adjacent rotor permanent magnets 5, and between any two adjacent magnetic focusing rings 71.

[0057] The magnetic focusing ring 71 serves to concentrate the permanent magnet flux and improve passive stiffness and vibration damping effect; the non-magnetic insulating ring 72 serves to separate adjacent magnetic focusing rings 71, adjacent stator permanent magnets 4 and adjacent rotor permanent magnets 5, so as to further improve structural stiffness and stability.

[0058] In some embodiments, the magnetic ring 71 is made of a high magnetic permeability material.

[0059] The magnetic ring 71, made of high permeability material, can further concentrate the permanent magnet flux to penetrate the conductor damping disk 6, thereby increasing the radial eddy current damping effect while improving the passive stiffness.

[0060] Specifically, high permeability materials can be selected from electrical pure iron or permalloy, etc.; the thickness of the magnetic ring 71 can be the same as the thickness of the rotor permanent magnet 5.

[0061] In some embodiments, see Figure 4The active-passive combined magnetic bearing structure also includes a stator permanent magnet 28 and a rotor permanent magnet 29; the stator permanent magnet 28 is coaxially sleeved outside the rotor shaft 21 and fixed to the other end of the stator magnetic conductor 1; the stator permanent magnet 28 is coaxially sleeved on the rotor shaft 21 and corresponds to the side of the stator permanent magnet 28 away from the stator magnetic conductor 1; both the stator permanent magnet 28 and the rotor permanent magnet 29 are axially magnetized and opposite magnetic poles are opposite to each other, so as to provide radial passive restoring force for the rotor shaft 21; the stator permanent magnet 28 and the stator permanent magnet 4 are arranged with the same magnetic poles opposite to each other along the axial direction of the stator magnetic conductor 1.

[0062] Specifically, the stator permanent magnet 28 and the rotor permanent magnet 29 are arranged axially at intervals, and the interval between the stator permanent magnet 28 and the rotor permanent magnet 29 constitutes an axial passive adjustment gap.

[0063] The combination of stator permanent magnet 28 and rotor permanent magnet 29 forms a radial passive magnetic bearing, which forms a structure in which radial passive magnetic bearings are symmetrically arranged at both ends of stator magnetic conductor 1, further increasing the stability of rotor shaft 21 operation; stator permanent magnet 28 and stator permanent magnet 14 cooperate to make the magnetic field distribution in the preset axial active adjustment gap 121 more balanced.

[0064] It should be noted that stator permanent magnet 4, rotor permanent magnet 5, stator permanent magnet 8, and rotor permanent magnet 9 are all annular and can have the same thickness, and are all axially magnetized. The radial passive magnetic bearings are divided into two groups: one group includes a pair of stator permanent magnet 4 and rotor permanent magnet 5, and the other group includes a pair of stator permanent magnet 8 and rotor permanent magnet 9; the two groups of radial passive magnetic bearings are symmetrically arranged at both ends of the stator magnetic conductor 1 along its axial direction. The polarity relationship between the stator and rotor permanent magnets allows the permanent magnet flux to form a loop, creating a radial restoring force between the stator and rotor, thus achieving radial passive levitation.

[0065] For details, see Figure 5 and Figure 6 The working principle of the active axial control of rotor shaft 21 is as follows: Assuming rotor shaft 21 is placed vertically, Figure 5 The solid line loops with arrows represent the magnetic flux paths generated by stator permanent magnet 4 and rotor permanent magnet 5, as well as stator permanent magnet 8 and rotor permanent magnet 9. Magnetic fluxes in opposite directions are generated in the air gaps on both sides of the thrust plate 22, which can be labeled φp_up and φp_down. The magnetic flux path generated by the energized axial control coil 3 is as follows... Figure 6As shown by the dashed loop with arrows, magnetic fluxes of the same direction are generated in the air gaps on both sides of the thrust plate 22, which can be labeled φiup and φidown. Therefore, the total magnetic flux in the air gaps on both sides of the thrust plate 22 is: φpup + φiup on the upper side and φpdown - φidown on the lower side. Obviously, the magnetic flux on the upper side of the thrust plate 22 is higher than that on the lower side; thus, an upward attractive force is generated on the thrust plate 22. Similarly, when a reverse current is passed through the axial control coil 3, a downward attractive force will be generated on the thrust plate 22. Therefore, by controlling the magnitude and direction of the current in the axial control coil 3, active axial control of the rotor shaft 21 can be achieved.

[0066] In some embodiments, both the rotor shaft 21 and the thrust disk 22 are made of magnetically conductive material.

[0067] The rotor shaft 21 and thrust disk 22 made of magnetically conductive material can reduce the magnetic loss of the permanent magnet circuit formed by stator permanent magnet 4 and rotor permanent magnet 5, as well as the permanent magnet circuit formed by stator permanent magnet 8 and rotor permanent magnet 9, which is conducive to miniaturizing the permanent magnet structure.

[0068] Specifically, the rotor shaft 21 and thrust disk 22 can be made of materials such as 40Cr and GCr15.

[0069] In some embodiments, the stator permanent magnet 4 and the rotor permanent magnet 5 are both made of ferrite permanent magnet material or rare earth permanent magnet material.

[0070] In some embodiments, the conductor damping disk 6 is made of a high-conductivity material with a thickness of 1-2 mm. The high-conductivity material can be copper, meaning the conductor damping disk 6 can be a ring-shaped copper disk.

[0071] The conductor damping disk 6, made of high conductivity material, can generate large eddy currents in the conductor damping disk 6 when radial vibration occurs in the rotor shaft 21, thereby damping the radial vibration and achieving a stronger vibration suppression effect.

[0072] In some embodiments, the axial control coil 3 is made of copper wire with a diameter of 0.2mm-1mm.

[0073] In some embodiments, the preset axial active adjustment gap 121 is 0.1mm-1mm; the preset axial passive adjustment gap 61 is 1mm-2mm.

[0074] In some embodiments, the rotor assembly 2 further includes a magnetic ring 23; the magnetic ring 23 may be made of materials such as pure iron, 40Cr or GCr15; the magnetic ring 23 is sleeved on the rotor shaft 21, and the rotor permanent magnet 5, the rotor permanent magnet 9, the magnetic ring 71 and the conductor damping disk 6 are all fixedly connected to the rotor shaft 21 through the magnetic ring 23.

[0075] Specifically, the conductor damping plate 6 is attached and fixed to the end face of the magnetic ring 71 away from the rotor permanent magnet 5; the magnetic isolation ring 72 is coaxially nested and fixed with the corresponding stator permanent magnet 4, rotor permanent magnet 5 and magnetic ring 71 by a tight fit or adhesive bonding method.

[0076] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. In addition, those skilled in the art can combine and integrate the different embodiments or examples described in this specification.

[0077] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

Claims

1. A structure for an active and passive magnetic bearing with radial vibration damping effect, characterized in that, The application relates to a motor, which comprises the following components: a stator magnetic conductor (1) which is annular and internally provided with an annular cavity (11) extending in the circumferential direction; the inner wall of the ring hole of the stator magnetic conductor (1) is provided with an annular opening (12) extending in the circumferential direction and communicating with the annular cavity (11); a rotor assembly (2) which comprises a rotor shaft (21) and a thrust disc (22); the rotor shaft (21) is coaxially arranged in the ring hole of the stator magnetic conductor (1); the thrust disc (22) is coaxially sleeved on the outer circumferential wall of the rotor shaft (21) and movably penetrates the annular opening (12) on the outer circumferential side; the two side disc surfaces of the thrust disc (22) are both provided with a preset axial active adjustment gap relative to the inner wall surfaces of the corresponding annular openings (12); an axial control coil (3) which is coaxially nested in the annular cavity (11) and is used for forming an adjusting magnetic field between the opposite inner walls of the annular opening (12); a stator permanent magnet (4) and a rotor permanent magnet (5); the stator permanent magnet (4) is coaxially sleeved on the outside of the rotor shaft (21) and fixed on one end of the stator magnetic conductor (1) to form magnetic fields with opposite directions at the opposite inner wall surfaces of the annular opening (12); the rotor permanent magnet (5) is coaxially sleeved on the rotor shaft (21) and away from the side of the stator permanent magnet (4) which is away from the stator magnetic conductor (1); the rotor permanent magnet (5) and the stator permanent magnet (4) are both axially magnetized and have opposite magnetic poles to provide a radial passive restoring force for the rotor shaft (21); a conductor vibration suppression disc (6) which is coaxially sleeved on the rotor shaft (21) and located between the rotor permanent magnet (5) and the stator permanent magnet (4); the conductor vibration suppression disc (6) and the stator permanent magnet (4) are provided with a preset axial passive adjustment gap.

2. The active-passive magnetic bearing structure with radial vibration suppression according to claim 1, characterized in that, The stator permanent magnet (4) and the rotor permanent magnet (5) are both multiple; the multiple stator permanent magnets (4) are annular and concentrically and radially spaced apart and all fixed on one end of the stator magnetic conductor (1); the multiple rotor permanent magnets (5) are annular and concentrically and radially spaced apart and all sleeved on the rotor shaft (21); the multiple rotor permanent magnets (5) are axially one-to-one corresponding to the multiple stator permanent magnets (4); the conductor vibration suppression disc (6) is corresponding to the multiple stator permanent magnets (4) and the multiple rotor permanent magnets (5).

3. The active-passive magnetic bearing structure with radial vibration suppression according to claim 2, characterized in that, The motor further comprises a magnetic gathering and separating assembly (7) which comprises a magnetic gathering ring (71) and a magnetic separating ring (72); the end of the multiple rotor permanent magnets (5) close to the conductor vibration suppression disc (6) is provided with the magnetic gathering ring (71); the magnetic separating ring (72) is arranged between any two adjacent stator permanent magnets (4), any two adjacent rotor permanent magnets (5) and any two adjacent magnetic gathering rings (71).

4. The active-passive magnetic bearing structure with radial vibration suppression according to claim 3, wherein, The magnetic gathering ring (71) is made of a high magnetic permeability material.

5. The hybrid magnetic bearing structure according to claim 1, wherein The application further comprises a second stator permanent magnet (8) and a second rotor permanent magnet (9); the second stator permanent magnet (8) is coaxially sleeved outside the rotor shaft (21) and fixed at the other end of the stator magnetic conductor (1); the second stator permanent magnet (8) is coaxially sleeved on the rotor shaft (21) and corresponds to the side of the second stator permanent magnet (8) away from the stator magnetic conductor (1); the second stator permanent magnet (8) and the second rotor permanent magnet (9) are both axially magnetized and have opposite poles to provide radial passive restoring force for the rotor shaft (21); the second stator permanent magnet (8) and the first stator permanent magnet (4) are arranged with opposite poles along the stator magnetic conductor (1).

6. The active-passive magnetic bearing structure with radial vibration suppression according to claim 1, wherein, The rotor shaft (21) and the thrust disc (22) are both made of magnetic conductive material.

7. The hybrid magnetic bearing structure according to claim 1, wherein the radial vibration suppression function is provided by the passive magnetic bearing. The first stator permanent magnet (4) and the first rotor permanent magnet (5) are both made of ferrite permanent magnet material or rare earth permanent magnet material.

8. The active-passive magnetic bearing structure with radial vibration suppression according to claim 1, wherein, The conductor vibration suppression disc (6) is made of high conductivity material and has a thickness of 1-2 mm.

9. The active and passive magnetic bearing structure with radial vibration suppression according to claim 1, characterized in that, The axial control coil (3) is wound by copper wire with a wire diameter of 0.2-1 mm.

10. The active-passive magnetic bearing structure with radial vibration suppression according to claim 1, wherein, The preset axial active adjustment gap is 0.1-1 mm; and the preset axial passive adjustment gap is 1-2 mm.

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