A compressor high speed rotor package and compressor overcoming centrifugal forces

Abstract

The application provides a compressor high-speed rotor set overcoming centrifugal force and a compressor, and belongs to the technical field of high-speed rotor sets.The compressor high-speed rotor set comprises a high-speed gear shaft, the high-speed gear shaft comprises a driving section and two groups of connecting sections, the two groups of connecting sections are located at the two ends of the driving section and are integrally formed, a thrust disc is sleeved on one end of the two groups of connecting sections close to the driving section, and a first-stage impeller and a second-stage impeller are respectively sleeved on the other end of the two groups of connecting sections; wherein, a special-shaped matching hole is formed in the thrust disc, a special-shaped matching shaft section is arranged on the connecting section corresponding to the special-shaped matching hole, the cross section of the contact surface of the special-shaped matching hole and the special-shaped matching shaft section is in a runway shape, the cross section comprises two groups of straight line sections arranged in parallel, and the two ends of the two groups of straight line sections are connected to form a closed structure through circular arc transition sections respectively; when the device is decelerated during shutdown, the radial convergence of the straight line sections of the special-shaped matching hole is used to form radial compressive stress, and the loosening of the traditional circular matching caused by centrifugal force is avoided.

Description

Technical Field

[0001] This invention relates to the field of high-speed rotor assembly technology, and more specifically, to a high-speed rotor assembly and compressor for overcoming centrifugal force. Background Technology

[0002] In the operation of a high-speed compressor, in order to achieve gas compression and stable power transmission, the high-speed rotor assembly often needs to operate at high speed. At this time, an interference fit structure between the thrust disc and the high-speed gear shaft is required to limit the axial and circumferential displacement of the thrust disc, so as to avoid power transmission failure caused by thrust disc slippage and ensure the normal compression operation of the compressor.

[0003] However, the traditional high-speed rotor assembly uses an interference fit of "circular hole + circular shaft" for the thrust disc and high-speed gear shaft, which lacks the structural characteristics to guide centrifugal strain. As a result, during high-speed rotation (especially during deceleration at a stop), the thrust disc will generate significant dynamic load stress due to centrifugal force, and the inner hole of the thrust disc will show a uniform expansion trend. Meanwhile, the high-speed gear shaft has very small radial deformation due to the constraints of the impellers and bearings at both ends. Under the repeated action of centrifugal force, the interference fit between the thrust disc and the high-speed gear shaft is prone to loosening, which in turn causes sliding friction between the two. The high temperature generated by friction will aggravate the ablation failure of the thrust disc. In severe cases, the thrust disc will break off and be thrown out, which will affect the normal operation of the compressor and cause industrial production to be interrupted. Summary of the Invention

[0004] To address the aforementioned technical problems, this invention provides a high-speed rotor assembly and compressor that overcome centrifugal force, thereby solving the technical problem in the prior art where, when a traditional high-speed rotor assembly stops, the permanent magnet support becomes unstable, the rotor radially shifts, leading to gas seal wear and bearing failure.

[0005] The purpose and effectiveness of the high-speed rotor assembly of the compressor and the compressor in this invention, which overcome centrifugal force, are achieved by the following specific technical means: The present invention provides a high-speed rotor assembly for a compressor that overcomes centrifugal force, comprising a high-speed gear shaft, wherein the high-speed gear shaft includes a drive section and two sets of connecting sections, the two sets of connecting sections being located at both ends of the drive section and being integrally formed; The two sets of connecting sections are fitted with a thrust disk at one end near the drive section, and a first-stage impeller and a second-stage impeller are fitted at the other end respectively; The thrust plate has irregularly shaped mating holes, and an irregularly shaped mating shaft section is provided on the connecting section corresponding to the irregularly shaped mating holes. The cross-section of the contact surface between the irregularly shaped mating holes and the irregularly shaped mating shaft section is racetrack-shaped, which includes two sets of parallel straight segments, and the two ends of the two sets of straight segments are connected by arc transition sections to form a closed structure.

[0006] As a preferred embodiment, when the high-speed gear shaft is driven to rotate, the thrust disk exhibits a radial expansion tendency due to centrifugal inertial force: wherein, the straight segment of the irregularly shaped mating hole is constrained by this expansion tendency and radially converges towards the irregularly shaped mating shaft segment, forming radial compressive stress on the irregularly shaped mating shaft segment; The arc transition section of the irregularly shaped mating hole is displaced along the centrifugal expansion direction away from the irregularly shaped mating shaft section, and radial tensile stress is formed due to the tension characteristics of the arc structure.

[0007] As a preferred embodiment, an electromagnetic bearing is included, wherein bearing grooves are provided on both sets of connecting sections, the electromagnetic bearing is embedded in the bearing grooves, and the inner wall of the bearing grooves is provided with two sets of positioning steps for axial positioning of the electromagnetic bearings. Permanent magnet rings are provided on both sets of positioning steps, and permanent magnet support seats are fitted on the permanent magnet rings, forming an annular gap between the permanent magnet support seats and the permanent magnet rings.

[0008] In a preferred embodiment, the permanent magnet ring includes a first magnetic ring and a second magnetic ring; The first magnetic ring is a split structure, which is installed on the positioning step by bolts. Its outer wall is evenly provided with multiple sets of mortises along the circumference. The second magnetic ring is an integral structure, and its inner wall is evenly provided with multiple sets of tenons along the circumference. The tenon is mounted on the mortise by bolts.

[0009] As a preferred embodiment, the tenon at the end furthest from the second magnetic ring body is integrally formed with a wedge-shaped locking platform extending radially outward; Corresponding to the wedge-shaped locking platform, a matching wedge-shaped locking groove is provided on the mortise, and the mating surfaces of the wedge-shaped locking platform and the wedge-shaped locking groove are inclined at an angle of 15°-30°. The wedge-shaped card holder has heat dissipation blades integrally formed on one side.

[0010] In a preferred embodiment, the permanent magnet support base includes two sets of support rings, which are symmetrically arranged along the radial direction of the permanent magnet ring, and a levitation cavity is formed between the two sets of support rings, with the second magnet ring located in the levitation cavity; Both sets of support rings are provided with support magnetic rings on the side near the positioning step. The support magnetic rings, the first magnetic ring, and the second magnetic ring are all made of neodymium iron boron permanent magnet material. The mortise and the tenon are both made of titanium alloy. The magnetic poles on both sides of the support ring are aligned with the magnetic poles of the first and second magnetic rings on opposite sides.

[0011] As a preferred embodiment, the magnetic field formed by the first magnetic ring and the magnetic field formed by the supporting magnetic ring generate an axial repulsive force, which is used to apply a reverse thrust toward the positioning step to the first magnetic ring, so as to prevent the first magnetic ring from being dislodged from the installation position due to axial vibration during high-speed rotation. The magnetic field formed by the second magnetic ring and the magnetic field formed by the supporting magnetic ring generate a radial repulsive force, which is used to provide a radially inward constraint force for the second magnetic ring, counteracting the radial expansion tendency of the second magnetic ring caused by centrifugal force, and helping to maintain the central position of the second magnetic ring in the suspension cavity.

[0012] As a preferred embodiment, the support ring is provided with multiple sets of magnetohydrodynamic damping rods along the circumferential direction near the side away from the positioning step. The movable rod of the magnetohydrodynamic damping rod is provided with a magnetic sheet, and a return spring is sleeved on the magnetohydrodynamic damping rod.

[0013] In a preferred embodiment, the magnetic sheet is L-shaped, and a U-shaped cavity is formed between two adjacent sets of magnetic sheets. The second magnetic ring is located within the U-shaped cavity, and the magnetic poles of the opposite surfaces of the magnetic sheet and the second magnetic ring are aligned. The repulsive force generated by the magnetic field formed by the magnetic sheet and the magnetic field formed by the second magnetic ring is used to suppress the offset when the high-speed gear shaft deviates.

[0014] A compressor includes a housing, within which a high-speed rotor assembly for overcoming centrifugal force is mounted.

[0015] Compared with the prior art, the present invention has the following beneficial effects: 1. This invention, through the setting of the racetrack-shaped irregular mating hole of the thrust disc and the irregular mating shaft section of the connecting section, enables the device to form radial compressive stress by utilizing the radial convergence of the straight section of the irregular mating hole during shutdown and deceleration. This avoids the loosening of the fit caused by centrifugal force in traditional circular fits. The device can eliminate the sliding friction between the thrust disc and the high-speed gear shaft through this self-reinforcing fit effect, thus completely solving the problems of thrust disc ablation failure and breakage. This improves the fit stability of the device in start-stop cycles and the continuous operation capability of the compressor.

[0016] 2. When using this device, the device can achieve dual support of "electromagnetic dynamic adjustment + permanent magnet static preload" through the coordinated arrangement of electromagnetic bearings, permanent magnet rings and permanent magnet support bases. The axial repulsion between the first magnetic ring and the support magnetic ring prevents them from dislodging from the installation position, and the radial repulsion between the second magnetic ring and the support magnetic ring counteracts centrifugal expansion. This prevents the device from becoming unstable in the permanent magnet support and the rotor from radially shifting, thus improving the device's resistance to centrifugal force. Furthermore, this coordinated support enables the device to prevent gas seal wear and bearing failure, reduce downtime caused by component damage, and improve the device's operational reliability and industrial production continuity.

[0017] 3. By setting up a magnetorheological damping rod and an L-shaped magnetic sheet, the present invention enables the device to quickly suppress the offset when the high-speed gear shaft deviates by utilizing the repulsive force between the magnetic sheet and the second magnetic ring. The device can also buffer the instantaneous vibration during shutdown by using a return spring to assist the moving rod of the magnetorheological damping rod in resetting. This reduces the impact of the rotor assembly on the gas seal and bearings, improves the device's anti-interference ability and component protection ability, extends the service life of vulnerable parts such as gas seals and bearings, and reduces the compressor maintenance cost. Attached Figure Description

[0018] Figure 1 This is a schematic diagram of the compressor structure of the invention; Figure 2 This is a schematic diagram of the high-speed rotor assembly structure of the invention; Figure 3 This is a schematic diagram of the internal structure of the high-speed rotor assembly of the invention; Figure 4 This is a schematic diagram of the thrust disk of the invention; Figure 5 This is a schematic diagram of the stress distribution structure of the thrust disk of the invention; Figure 6 This is a schematic diagram of the permanent magnet ring and permanent magnet support base of the invention. Figure 7 yes Figure 6 Enlarged view of region a in the middle; Figure 8 yes Figure 6 Enlarged view of region b in the middle; Figure 9 This is a schematic diagram of the internal structure of the permanent magnet ring and permanent magnet support base of the invention; Figure 10 This is a schematic diagram of the radial strain of the thrust disc of the invention.

[0019] In the diagram, the correspondence between component names and their corresponding reference numerals is as follows: 1011. Drive section; 1012. Connecting section; 10121. Irregularly shaped mating shaft section; 10122. Bearing groove; 10123. Positioning step; 102. Thrust plate; 1021. Irregularly shaped mating hole; 103. First-stage impeller; 104. Second-stage impeller; 105. Electromagnetic bearing; 106. Permanent magnet ring; 1061. First magnetic ring; 1062. Second magnetic ring; 1063. Tenon; 10631. Wedge-shaped slot; 1064. Tenon; 10641. Wedge-shaped mounting platform; 10642. Heat dissipation blade; 107. Permanent magnet support base; 1071. Support ring; 1072. Support magnetic ring; 108. Magnetorheological damping rod; 109. Magnetic sheet; 111. Return spring; 201. Suspension cavity; 202. U-shaped cavity; 301. Outer shell. Detailed Implementation

[0020] The embodiments of the present invention will be described in further detail below with reference to the accompanying drawings and examples. The following examples are used to illustrate the technical solutions of the present invention, but should not be used to limit the scope of protection of the present invention.

[0021] Example

[0022] like Figures 1 to 5 As shown, the present invention provides a high-speed rotor assembly for a compressor that overcomes centrifugal force, including a high-speed gear shaft. The high-speed gear shaft includes a drive section 1011 and two sets of connecting sections 1012. The two sets of connecting sections 1012 are located at both ends of the drive section 1011 and are integrally formed. A thrust disk 102 is sleeved on one end of the two sets of connecting sections 1012 near the drive section 1011, and a first-stage impeller 103 and a second-stage impeller 104 are respectively sleeved on the other end. The thrust disk 102 has a shaped mating hole 1021. Corresponding to the shaped mating hole 1021, a shaped mating shaft section 10121 is provided on the connecting section 1012. The cross-section of the contact surface between the shaped mating hole 1021 and the shaped mating shaft section 10121 is racetrack-shaped, which includes two sets of parallel straight segments. The two ends of the two sets of straight segments are connected by arc transition sections to form a closed structure.

[0023] Specifically, the irregularly shaped mating shaft section 10121 and the connecting section 1012 are integrally formed structures, made of high-strength alloy through forging and machining. Its racetrack-shaped cross-section is adapted to the irregularly shaped mating hole 1021 of the thrust disc 102. Two sets of parallel straight segments constitute the main support structure of the mating surface, ensuring close contact between the two surfaces; the rounded transition sections at both ends prevent sharp-angle stress concentration on the mating surface and disperse the centrifugal load generated during high-speed rotation.

[0024] From an assembly logic perspective, the thrust disc 102 and the irregularly shaped mating shaft section 10121 are fixed with an interference fit. During assembly, a low-temperature cold-fitting process is used to temporarily expand the irregularly shaped mating hole 1021, which then recovers to its initial fit at room temperature after being fitted onto the shaft section. This assembly method ensures both the initial tightness of the fit and reserves space for stress adjustment during subsequent high-speed operation. Compared to traditional circular fits that rely solely on interference fit to maintain tightness, the core advantage of this racetrack-shaped structure lies in the active guidance and utilization of centrifugal force: when the rotor rotates at high speed, the stress induced by centrifugal force exhibits a differentiated distribution along the cross-section—radial compressive stress is generated in the direction parallel to the straight line segment, causing the inner hole of the thrust disc 102 to tend to contract in this direction; while the slight expansion tendency in the direction of the arc transition segment is suppressed. Since the high-speed gear shaft is constrained by the impellers and bearings at both ends, the radial deformation is minimal. The contraction of the thrust disc 102 in the direction of the straight line segment directly enhances the tightness of the fit with the shaft section, forming a self-reinforcing effect of "the higher the speed, the tighter the fit".

[0025] like Figure 5 , Figure 10As shown, when the high-speed gear shaft is driven to rotate, the thrust disk 102 has a radial expansion tendency due to centrifugal inertial force: the straight segment of the irregular mating hole 1021 is constrained by this expansion tendency and radially converges towards the irregular mating shaft segment 10121, forming radial compressive stress on the irregular mating shaft segment 10121. The arc transition section of the irregular mating hole 1021 is displaced along the centrifugal expansion direction in a direction away from the irregular mating shaft section 10121, and radial tensile stress is formed due to the tension characteristics of the arc structure.

[0026] Specifically, when the high-speed gear shaft is driven to rotate, the thrust disk 102 tends to expand radially due to centrifugal inertial force. However, this tendency will exhibit directional constraint and stress differentiation due to the differentiated structural characteristics of the irregular mating hole 1021, which consists of a "straight line segment + circular arc transition segment". From the perspective of the straight section of the irregularly shaped mating hole 1021, it is in surface contact with the irregularly shaped mating shaft section 10121. Furthermore, the high-speed gear shaft is constrained by the first-stage impeller 103, the second-stage impeller 104, and the bearings at both ends, resulting in minimal radial deformation. This effectively provides a "rigid limiting reference" for the straight section. When the thrust disk 102 as a whole has a tendency to expand radially, the expansion of the straight section is directly blocked by the irregularly shaped mating shaft section 10121. Since the planar structure of the straight section lacks additional deformation buffer space, the expansion trend, once constrained, will reverse and transform into a radially converging motion towards the irregularly shaped mating shaft section 10121. This convergence further reduces the mating clearance between the straight section and the shaft section, thereby creating a continuous radial compressive stress on the irregularly shaped mating shaft section 10121. This compressive stress can firmly "lock" the shaft section, preventing circumferential sliding or axial movement between the thrust disk 102 and the high-speed gear shaft.

[0027] Let's examine the arc transition section of the irregularly shaped mating hole 1021: its arc structure inherently possesses certain tension characteristics. Driven by centrifugal inertial force, it can generate a slight displacement along the centrifugal expansion direction (away from the center of the high-speed gear shaft). However, this displacement is not an unconstrained "free expansion"—the two ends of the arc transition section are seamlessly connected to the straight section, and the radial convergence of the straight section will create a tensile limit on the arc transition section, strictly controlling the displacement of the arc transition section within a very small range. At the same time, the tension characteristics of the arc structure will convert the centrifugal expansion force into radial tensile stress, which can be evenly distributed on the arc surface, avoiding stress concentration at a certain point that could damage the mating surface; more importantly, the slight displacement of the arc transition section will not affect the fit between the straight section and the shaft section, but rather, by "bearing" part of the expansion force, it further enhances the radial convergence effect of the straight section.

[0028] like Figures 6 to 9As shown, the device includes an electromagnetic bearing 105. Each of the two connecting sections 1012 has a bearing groove 10122. The electromagnetic bearing 105 is embedded in the bearing groove 10122. The inner wall of the bearing groove 10122 has two sets of positioning steps 10123 for axially limiting the electromagnetic bearing 105. Each of the two positioning steps 10123 has a permanent magnet ring 106. A permanent magnet support seat 107 is sleeved on the permanent magnet ring 106. An annular gap is formed between the permanent magnet support seat 107 and the permanent magnet ring 106.

[0029] Specifically, the bearing grooves 10122 on the two sets of connecting sections 1012 provide an installation reference for the electromagnetic bearing 105, ensuring that the electromagnetic bearing 105 is arranged coaxially with the high-speed gear shaft, providing stable support for the high-speed rotation of the rotor assembly. The two sets of positioning steps 10123 on the inner wall of the bearing groove 10122 are symmetrically distributed along the axial direction, and their end faces are in contact with the two end faces of the electromagnetic bearing 105. This directly restricts the axial movement of the electromagnetic bearing 105 caused by axial force during high-speed rotation, preventing the electromagnetic bearing 105 from colliding and wearing with the connecting section 1012 or other components, thus laying the foundation for the axial stability of the rotor assembly.

[0030] The permanent magnet ring 106 mounted on the positioning step 10123 and the permanent magnet support base 107 form a "ring-type" auxiliary support structure. The permanent magnet support base 107 is fixed to the outer housing or fixed bracket. The annular gap reserved between its inner wall and the outer wall of the permanent magnet ring 106 provides the necessary space for the dynamic radial adjustment of the electromagnetic bearing 105, avoiding rigid interference between the permanent magnet components and the electromagnetic bearing 105. At the same time, it can provide static radial preload for the high-speed gear shaft through the magnetic repulsion or attraction between the permanent magnet ring 106 and the permanent magnet support base 107. This preload can initially offset part of the radial expansion trend caused by centrifugal force, reduce the dynamic adjustment load of the electromagnetic bearing 105 under high-speed conditions, and improve the support response speed.

[0031] When the high-speed gear shaft is driven to rotate, the electromagnetic bearing 105 and the permanent magnet structure work together: on the one hand, the electromagnetic bearing 105 outputs dynamic electromagnetic force by detecting the radial displacement of the rotor in real time, compensating for the slight radial offset caused by centrifugal force, and ensuring that the rotor is always in a coaxial rotation state; on the other hand, the annular gap between the permanent magnet ring 106 and the permanent magnet support seat 107, in conjunction with the magnetic effect, can buffer the instantaneous impact during the adjustment process of the electromagnetic bearing 105, while avoiding the overtravel of the electromagnetic bearing 105 due to excessive centrifugal force. This combination of "electromagnetic dynamic adjustment + permanent magnet static pre-tightening" support method complements the racetrack-shaped irregular fit structure of the thrust plate 102—the former suppresses the lateral movement caused by centrifugal force from the radial support dimension, while the latter enhances the fit tightness between the thrust plate 102 and the shaft section from the fit and fastening dimension, ultimately overcoming the damage of centrifugal force to the rotor assembly from multiple dimensions, and further improving the operating stability and service life of the compressor's high-speed rotor assembly.

[0032] The permanent magnet ring 106 includes a first magnetic ring 1061 and a second magnetic ring 1062. The first magnetic ring 1061 is a split structure and is installed on the positioning step 10123 by bolts. Its outer wall is evenly provided with multiple sets of mortises 1063 along the circumferential direction. The second magnetic ring 1062 is an integral structure and its inner wall is evenly provided with multiple sets of tenons 1064 along the circumferential direction. The tenons 1064 are installed on the mortises 1063 by bolts.

[0033] Specifically, the first magnetic ring 1061 adopts a split structure. The core purpose is to adapt to the installation scenario of the bearing groove 10122 and the positioning step 10123 of the connecting section 1012. Compared with the integrated magnetic ring, the split structure can be disassembled into two sets of arc-shaped units. With the electromagnetic bearing 105 already embedded in the bearing groove 10122, it can avoid the electromagnetic bearing 105 components and be gradually spliced ​​and installed from the side of the positioning step 10123. There is no need to perform additional processing and diameter expansion on the bearing groove 10122 or the connecting section 1012, which reduces the assembly difficulty and interference with the original structure. During installation, each arc-shaped unit is fastened to the pre-set screw holes of the positioning step 10123 with bolts. The bolts are evenly distributed along the circumference of the positioning step 10123 (arranged alternately with the mortise 1063), which ensures the fit between the first magnetic ring 1061 and the positioning step 10123, and avoids mutual interference between the bolts and the mortise 1063 when under force. At the same time, the uniformity control of the split splicing ensures the overall coaxiality of the first magnetic ring 1061, laying the foundation for the subsequent cooperation with the second magnetic ring 1062.

[0034] Multiple sets of mortises 1063 on the outer wall of the first magnetic ring 1061 are evenly spaced along the circumference. The number of mortises 1063 matches the number of tenons 1064 on the inner wall of the second magnetic ring 1062. Each set of mortises 1063 has a flat mating surface and bolt holes on its end face. The mating surface is used to mate with the end face of the tenon 1064, ensuring maximum contact area and reducing local stress concentration. The bolt holes are coaxial with the corresponding holes of the tenons 1064, facilitating rigid connection with bolts. The radial height of the mortises 1063 matches the radial length of the tenons 1064, so that after connection, the first magnetic ring 1061 and the second magnetic ring 1062 can form a continuous annular permanent magnet structure, avoiding magnetic field breakage due to connection gaps and ensuring the stability of subsequent magnetic interaction with the permanent magnet support 107.

[0035] The second magnetic ring 1062 adopts an integrated ring structure, which has the advantage of higher overall rigidity. It can resist radial expansion deformation caused by centrifugal force during high-speed rotation and avoid the accumulation of deformation caused by splicing gaps in the split structure. The tenon 1064 on the inner wall of the second magnetic ring 1062 corresponds one-to-one with the mortise 1063 of the first magnetic ring 1061. The cross-sectional profile of the tenon 1064 fits perfectly with the mating groove of the mortise 1063 (such as rectangular or trapezoidal), ensuring no radial wobble during assembly. The tenon 1064 is fastened by bolts passing through the bolt holes of itself and the mortise 1063. The bolts are made of titanium alloy, the same material as the mortise 1063 and the tenon 1064, which matches the strength and thermal expansion coefficient of both and avoids electrochemical corrosion when different materials come into contact. At the same time, the lightweight characteristics of titanium alloy can reduce the additional centrifugal load on the tenon 1064 and the mortise 1063.

[0036] This combination of a "split first magnetic ring 1061 + integrated second magnetic ring 1062," along with a "mortise and tenon positioning + bolt fastening" connection method, provides dual protection: on the one hand, the mortise and tenon structure achieves circumferential and radial positioning of the first magnetic ring 1061 and the second magnetic ring 1062, transmitting torque during high-speed rotation and reducing shear force on the bolts; on the other hand, bolt fastening further strengthens the connection rigidity of the two, preventing the tenon 1064 and the mortise 1063 from separating under centrifugal force. Simultaneously, this structure allows the permanent magnet ring 106 as a whole to work synergistically under stress—the integrated structure of the second magnetic ring 1062 can evenly transmit centrifugal force to each tenon 1064, then distribute it to the first magnetic ring 1061 through the mortise 1063, and finally transmit it from the first magnetic ring 1061 to the positioning step 10123, forming a stable force transmission path that resists the damage to the structural integrity of the permanent magnet ring 106 by centrifugal force, ensuring stable magnetic interaction between it and the permanent magnet support 107.

[0037] One end of the tenon 1064 away from the body of the second magnetic ring 1062 is integrally formed with a wedge-shaped locking platform 10641 along the radial outward direction; corresponding to the wedge-shaped locking platform 10641, a matching wedge-shaped locking groove 10631 is provided on the tenon 1063, and the mating surfaces of the wedge-shaped locking platform 10641 and the wedge-shaped locking groove 10631 are inclined at an angle of 15°-30°; a heat dissipation blade 10642 is integrally formed on one side of the wedge-shaped locking platform 10641.

[0038] Specifically, the tenon 1064 and the wedge-shaped mounting plate 10641 are manufactured using an integral molding process, and the material is consistent with that of the tenon 1064. This can prevent the spliced ​​structure from breaking or loosening due to centrifugal force during high-speed rotation, while ensuring the overall rigidity of the wedge-shaped mounting plate 10641 and the tenon 1064 to meet the stress requirements of long-term high-speed operation. The wedge-shaped locking platform 10641 extends radially outward along the tenon 1064, and its cross-sectional profile is perfectly matched with the wedge-shaped locking groove 10631 of the mortise 1063. The inclination angle of the groove is consistent with the 15°-30° of the locking platform's mating surface. During assembly, the inclination surface can guide the wedge-shaped locking platform 10641 to slide smoothly into the groove, reducing the difficulty of alignment. When the high-speed gear shaft rotates, the tenon 1064 will have a radial expansion tendency due to centrifugal force. The inclination surface of the wedge-shaped locking platform 10641 will fit with the inclination surface of the groove. The higher the rotation speed, the greater the fitting pressure caused by centrifugal force, forming a self-reinforcing effect of "the higher the rotation speed, the tighter the fit". This supplements the tightness of the bolt connection and prevents the tenon 1064 and the mortise 1063 from sliding relative to each other in the circumferential or radial direction, further strengthening the connection stability of the first magnetic ring 1061 and the second magnetic ring 1062.

[0039] The heat dissipation blades 10642 on one side of the wedge-shaped mounting plate 10641 are also integrally formed. The blades are evenly distributed along the circumference of the wedge-shaped mounting plate 10641 (usually corresponding to the number of tenons 1064 and mortises 1063, such as 4-8 sets). The blades are arc-shaped, and the arc direction is consistent with the rotation direction of the high-speed gear shaft, which can reduce airflow resistance. When the high-speed gear shaft is driven to rotate, the heat dissipation blades 10642 rotate synchronously with the wedge-shaped mounting plate 10641, causing the surrounding air to flow along the arc surface of the blades, forming an airflow convection along the radial direction of the permanent magnet ring 106. This airflow can directly carry away the heat generated by friction at the tenon and mortise connection parts (bolts, the contact surface between the wedge-shaped mounting plate 10641 and the slot), and at the same time, it can also help dissipate the hysteresis loss heat generated when the first magnetic ring 1061 and the second magnetic ring 1062 are working, avoiding local overheating that could cause thermal expansion and deformation of the titanium alloy material, affecting the tenon and mortise fit clearance or the attenuation of the magnetic performance of the permanent magnet ring 106. In addition, the presence of the heat dissipation blades 10642 does not increase the radial dimension of the permanent magnet ring 106. Extending along the side of the wedge-shaped mounting plate 10641, it does not interfere with the annular gap between the permanent magnet support 107 and the permanent magnet ring 106, ensuring the stable transmission of magnetic repulsion / magnetic attraction, taking into account both heat dissipation function and magnetic effect, and providing thermal management guarantee for the rotor assembly to overcome centrifugal force and maintain long-term stable operation.

[0040] The permanent magnet support base 107 includes two sets of support rings 1071, which are symmetrically arranged along the radial direction of the permanent magnet ring 106. A suspension cavity 201 is formed between the two sets of support rings 1071, and the second magnetic ring 1062 is located in the suspension cavity 201. Each of the two sets of support rings 1071 is provided with a support magnetic ring 1072 on the side near the positioning step 10123. The support magnetic ring 1072, the first magnetic ring 1061, and the second magnetic ring 1062 are all made of neodymium iron boron permanent magnet material. The tenon 1063 and the mortise 1064 are both made of titanium alloy. The magnetic poles on both sides of the support ring 1071 are consistent with the magnetic poles of the first magnetic ring 1061 and the second magnetic ring 1062 on the opposite side.

[0041] Specifically, the two sets of support rings 1071 are symmetrically distributed along the radial direction (i.e., perpendicular to the axis of the high-speed gear shaft) of the permanent magnet ring 106, centered on the axis of the high-speed gear shaft. They are typically divided into an inner support ring 1071 and an outer support ring 1071—the inner support ring 1071 is closer to the high-speed gear shaft, and the outer support ring 1071 is farther from the high-speed gear shaft, maintaining a fixed relative position and together forming an annular suspension cavity 201. The radial width of the suspension cavity 201 matches the radial thickness of the second magnetic ring 1062, ensuring that the second magnetic ring 1062 can be completely embedded within the suspension cavity 201 and maintains a uniform gap with the inner walls of both sets of support rings 1071. This provides installation space for the second magnetic ring 1062, avoids rigid collisions with the support rings 1071 during high-speed rotation, and reserves the necessary distance for stable transmission of magnetic effects.

[0042] The two sets of support rings 1071 are located on the side of the positioning step 10123, that is, the inner end face of the inner support ring 1071 and the inner end face of the outer support ring 1071 are equipped with support magnetic rings 1072 by means of inlay or bolt fixing. The support magnetic rings 1072, the first magnetic ring 1061 and the second magnetic ring 1062 are all made of neodymium iron boron permanent magnet material. This material has the characteristics of high remanence and high coercivity. It can maintain a stable magnetic field for a long time under harsh working conditions such as high speed rotation and vibration, and avoid magnetic failure due to magnetic field attenuation. It is suitable for the working requirements of the high-speed rotor assembly of the compressor. The magnetic pole arrangement of the supporting magnetic ring 1072 must strictly follow the principle that "the magnetic poles on both sides of the supporting ring 1071 are consistent with the magnetic poles of the first magnetic ring 1061 and the second magnetic ring 1062 on the opposite side." That is, the magnetic pole of the supporting magnetic ring 1072 facing the first magnetic ring 1061 is the same as the magnetic pole of the first magnetic ring 1061 facing the supporting magnetic ring 1072, which is the same as the magnetic pole of the first magnetic ring 1061 facing the supporting magnetic ring 1072, which is the same as the magnetic pole of the second magnetic ring 1062 facing the supporting magnetic ring 1072, which is also the same as the magnetic pole of the second magnetic ring 1062 facing the supporting magnetic ring 1072, which is the same as the magnetic pole of the second magnetic ring 1062 facing the supporting magnetic ring 1072. Through the magnetic principle of "mutual repulsion of like magnetic poles", a bidirectional stable repulsive force constraint is formed.

[0043] From the perspective of force and functional adaptation, the core function of this magnetic pole arrangement is reflected in two aspects: Firstly, the axial repulsive force between the supporting magnetic ring 1072 and the first magnetic ring 1061 can apply a reverse thrust towards the positioning step 10123 to the split first magnetic ring 1061, counteracting the tendency of the first magnetic ring 1061 to "detach from the positioning step 10123" caused by axial vibration during high-speed rotation. Combined with the bolted connection between the first magnetic ring 1061 and the positioning step 10123, a dual fixing effect of "rigid bolt fixing + axial limiting by magnetic repulsion" is formed, ensuring that the first magnetic ring 1061 always remains tightly attached to the positioning step 10123, preventing its axial displacement. The axial movement affects the overall structural stability of the permanent magnet ring 106; on the other hand, the radial repulsion between the supporting magnetic ring 1072 and the second magnetic ring 1062 can provide a radially inward (i.e. towards the axis of the high-speed gear shaft) constraint force for the integrated second magnetic ring 1062, directly counteracting the "radial expansion" tendency caused by centrifugal force when the second magnetic ring 1062 rotates at high speed, helping to maintain the central position of the second magnetic ring 1062 in the suspension cavity 201, avoiding its collision with the supporting ring 1071 due to centrifugal force deviation, and at the same time reducing the radial adjustment load of the electromagnetic bearing 105, forming a synergy with the support system of "electromagnetic dynamic adjustment + permanent magnet static preload".

[0044] Furthermore, the mortise 1063 and tenon 1064 are made of titanium alloy, which is compatible with the neodymium iron boron permanent magnet ring 106. Titanium alloy has the characteristics of being lightweight, high-strength, and having low magnetic permeability. Lightweighting can reduce the centrifugal load on the mortise 1063 and tenon 1064 when they rotate at high speed, avoiding additional radial expansion pressure on the permanent magnet ring 106. High strength can ensure that the tenon and mortise connection does not deform or break under the combined action of magnetic repulsion and centrifugal force. Low magnetic permeability can prevent the mortise 1063 and tenon 1064 from interfering with the magnetic field distribution between the permanent magnet ring 106 and the supporting magnetic ring 1072, ensuring stable transmission of magnetic repulsion and preventing magnetic field shielding or disorder. This further ensures the static pre-tightening and dynamic constraint effect of the permanent magnet support 107 on the high-speed rotor assembly.

[0045] The magnetic field formed by the first magnetic ring 1061 and the magnetic field formed by the supporting magnetic ring 1072 generate an axial repulsive force, which is used to apply a reverse thrust towards the positioning step 10123 to the first magnetic ring 1061 to prevent the first magnetic ring 1061 from being dislodged from the installation position due to axial vibration during high-speed rotation; the magnetic field formed by the second magnetic ring 1062 and the magnetic field formed by the supporting magnetic ring 1072 generate a radial repulsive force, which is used to provide a radially inward constraint force for the second magnetic ring 1062 to counteract the radial expansion tendency of the second magnetic ring 1062 caused by centrifugal force and help maintain the central position of the second magnetic ring 1062 in the suspension cavity 201.

[0046] Specifically, considering the axial repulsive force between the first magnetic ring 1061 and the supporting magnetic ring 1072: Since the first magnetic ring 1061 is a split structure and is bolted to the positioning step 10123, its relative position to the supporting magnetic ring 1072 is axially corresponding—the supporting magnetic ring 1072 is fixed on the side of the supporting ring 1071 near the positioning step 10123. The end face of the first magnetic ring 1061 facing the supporting magnetic ring 1072 is parallel to the end face of the supporting magnetic ring 1072 facing the first magnetic ring 1061 and the spacing is uniform. Moreover, the magnetic poles of the two are strictly arranged to be of the same name and opposite. For example, the magnetic pole of the first magnetic ring 1061 facing the supporting magnetic ring 1072 is the N pole, and the magnetic pole of the supporting magnetic ring 1072 facing the first magnetic ring 1061 is also the N pole. Based on the magnetic principle of repulsion between like magnetic poles, an axial repulsive force is generated between the first magnetic ring 1061 and the supporting magnetic ring 1072. The direction of this repulsive force is exactly opposite to the "axial separation tendency" that may occur when the first magnetic ring 1061 rotates at high speed: when the high-speed gear shaft rotation causes axial vibration, and the first magnetic ring 1061 is at risk of separating axially away from the positioning step 10123 (i.e., towards the supporting magnetic ring 1072), the axial repulsive force will directly exert a reverse thrust on the first magnetic ring 1061 towards the positioning step 10123, firmly "pressing" the first magnetic ring 1061 into the mounting position of the positioning step 10123. This magnetic repulsive force and the rigid fixation of the bolts form a double guarantee, which not only avoids the fatigue failure of the bolts due to long-term axial vibration shear force, but also eliminates the hidden danger of the first magnetic ring 1061 separating from the mounting position due to axial vibration, ensuring the assembly stability of the first magnetic ring 1061 as the basic assembly of the permanent magnet structure.

[0047] Next, consider the radial repulsive force between the second magnetic ring 1062 and the supporting magnetic ring 1072: The second magnetic ring 1062 is an integral structure located within the suspension cavity 201. Its outer circumference corresponds radially to the supporting magnetic rings 1072 on the two supporting rings 1071. The two supporting magnetic rings 1072 are evenly distributed along the circumference of the suspension cavity 201, and the magnetic poles of the supporting magnetic rings 1072 facing the second magnetic ring 1062 are also opposite to each other (e.g., both are S poles). During high-speed rotation, the second magnetic ring 1062 will expand radially outward (i.e., away from the axis of the high-speed gear shaft) due to centrifugal force. At this time, the radial repulsive force generated between the two supporting magnetic rings 1072 and the second magnetic ring 1062 has a resultant force pointing radially towards the axis of the high-speed gear shaft, forming a "radial inward constraint force" on the second magnetic ring 1062. This constraint force directly counteracts the radial expansion tendency of the second magnetic ring 1062, preventing it from colliding and wearing against the inner wall of the support ring 1071 of the suspension cavity 201 due to excessive expansion caused by centrifugal force. Simultaneously, because the support magnetic ring 1072 is uniformly distributed along its circumference, the radial repulsive force it generates is symmetrically distributed around the outer periphery of the second magnetic ring 1062, ensuring that the second magnetic ring 1062 always remains in the central position of the suspension cavity 201 and does not experience radial displacement due to uneven centrifugal force on one side. This radial repulsive force also helps reduce the radial adjustment load on the electromagnetic bearing 105—when the second magnetic ring 1062 slightly expands due to centrifugal force, the radial repulsive force can provide pre-constraint compensation, eliminating the need for the electromagnetic bearing 105 to frequently output dynamic adjustment force, further improving the operational stability of the second magnetic ring 1062 within the suspension cavity 201, and forming a synergistic effect with the dynamic support of the electromagnetic bearing 105.

[0048] The support ring 1071 is provided with multiple sets of magnetohydrodynamic damping rods 108 along the circumferential direction on the side close to the positioning step 10123. The movable rod of the magnetohydrodynamic damping rod 108 is provided with a magnetic sheet 109, and a return spring 111 is sleeved on the magnetohydrodynamic damping rod 108.

[0049] The magnetic sheet 109 is L-shaped, and a U-shaped cavity 202 is formed between two adjacent sets of magnetic sheets 109. The second magnetic ring 1062 is located in the U-shaped cavity 202, and the magnetic poles of the opposite surfaces of the magnetic sheet 109 and the second magnetic ring 1062 are aligned. The repulsive force generated by the magnetic field formed by the magnetic sheet 109 and the magnetic field formed by the second magnetic ring 1062 is used to suppress the offset when the high-speed gear shaft deviates.

[0050] Specifically, the installation and structure of the magnetofluid damping rod 108 on the support ring 1071 are primarily intended to further buffer the radial displacement of the high-speed rotor assembly caused by centrifugal force fluctuations or instantaneous vibrations. Specific details are as follows: From an installation layout perspective, the magnetohydrodynamic damping rods 108 are evenly distributed along the circumference of the support ring 1071 on the side "away from the positioning step 10123," ensuring a symmetrical distribution of damping force along the circumference of the support ring 1071. This symmetry prevents the support ring 1071 from tilting due to uneven damping force on one side, or the second magnetic ring 1062 from shifting due to damping on one side, thus laying a structural foundation for stable output of subsequent damping action. The fixed end of the magnetohydrodynamic damping rod 108 is rigidly connected to the support ring 1071 (e.g., by welding or bolting), while the movable rod is set along the radial direction of the support ring 1071 (i.e., consistent with the radial direction of the high-speed gear shaft), allowing for free radial extension and retraction to ensure responsiveness to radial offset of the second magnetic ring 1062.

[0051] From the perspective of structural composition and initial state, a magnetic plate 109 is fixedly mounted on the movable rod of the magnetohydrodynamic damping rod 108. The magnetic pole direction of the magnetic plate 109 is aligned with the magnetic pole direction of the second magnetic ring 1062 (e.g., both are N poles or both are S poles), and the position of the magnetic plate 109 corresponds to the outer periphery of the second magnetic ring 1062, ensuring that the two can form a stable magnetic repulsion force. At the same time, a return spring 111 is sleeved on the outside of the movable rod of the magnetohydrodynamic damping rod 108. One end of the return spring 111 abuts against the fixed end of the magnetohydrodynamic damping rod 108, and the other end abuts against the magnetic plate 109 on the movable rod (or the limiting step of the movable rod). In the initial state, the return spring 111 is in a slightly pre-tightened state. This pre-tightening ensures that the movable rod always maintains the initial position "close to the second magnetic ring 1062", ensuring that a stable initial magnetic repulsion force gap is maintained between the magnetic plate 109 and the second magnetic ring 1062, and avoiding damping response delay due to loosening of the movable rod.

[0052] From the working mechanism perspective, when the high-speed rotor assembly experiences a sudden increase in centrifugal force (such as during start-up and shutdown) or airflow disturbance, causing the second magnetic ring 1062 to deflect radially: if the second magnetic ring 1062 moves closer to the magnetorheological damping rod 108 on one side, the repulsive force between its corresponding magnetic poles and the magnetic sheet 109 on that side will increase instantaneously, pushing the movable rod to extend and retract radially outward (away from the direction of the second magnetic ring 1062); at this time, the magnetorheological fluid (damping medium based on magnetorheological effect) inside the magnetorheological damping rod 108 will generate a viscous damping force due to the movement of the movable rod. This damping force can quickly consume the kinetic energy generated by the deflection of the second magnetic ring 1062, suppressing the further expansion of the deflection amplitude; at the same time, the movable rod will compress or stretch the return spring 111 during the extension and retraction process, and the elastic force generated by the return spring 111 will act in the opposite direction on the movable rod. After the deflection force weakens, the elastic force will push the movable rod to reset, driving the magnetic sheet 109 back to the initial position, so that the second magnetic ring 1062 returns to the central state of the suspension cavity 201.

[0053] A compressor includes a housing 301, within which a high-speed rotor assembly for overcoming centrifugal force is installed.

[0054] Specifically, the compressor housing 301 is made of high-strength alloy material and is coaxial with the high-speed rotor assembly that overcomes centrifugal force. This provides installation and protection space for the rotor assembly (including components such as high-speed gear shaft, thrust disk 102, first-stage impeller 103, second-stage impeller 104, electromagnetic bearing 105, permanent magnet ring 106, etc.) to prevent external interference when the rotor assembly rotates at high speed.

[0055] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A high-speed rotor assembly for a compressor that overcomes centrifugal force, comprising a high-speed gear shaft (101), the high-speed gear shaft (101) comprising a drive section (1011) and two sets of connecting sections (1012), the two sets of connecting sections (1012) being located at both ends of the drive section (1011) and being integrally formed, characterized in that: The two sets of connecting sections (1012) are fitted with a thrust disk (102) at one end near the drive section (1011), and a first-stage impeller (103) and a second-stage impeller (104) are fitted at the other end respectively. The thrust plate (102) has an irregularly shaped mating hole (1021), and a irregularly shaped mating shaft section (10121) is provided on the connecting section (1012) corresponding to the irregularly shaped mating hole (1021). The cross-section of the contact surface between the irregularly shaped mating hole (1021) and the irregularly shaped mating shaft section (10121) is similar to a racetrack shape, which includes two sets of parallel straight segments, and the two ends of the two sets of straight segments are connected by arc transition sections to form a closed structure.

2. The high-speed rotor assembly of a compressor that overcomes centrifugal force according to claim 1, characterized in that: When the high-speed gear shaft (101) is driven to rotate, the thrust disk (102) will have a radial expansion tendency due to centrifugal inertial force: the straight segment of the irregular mating hole (1021) is constrained by this expansion tendency and radially converges towards the irregular mating shaft segment (10121), forming radial compressive stress on the irregular mating shaft segment (10121). The arc transition section of the irregular mating hole (1021) is displaced along the centrifugal expansion direction in a direction away from the irregular mating shaft section (10121), and radial tensile stress is formed due to the tension characteristics of the arc structure.

3. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 1, characterized in that: The system includes an electromagnetic bearing (105), and two sets of connecting sections (1012) are provided with bearing grooves (10122). The electromagnetic bearing (105) is embedded in the bearing groove (10122). The inner wall of the bearing groove (10122) is provided with two sets of positioning steps (10123) for axially limiting the electromagnetic bearing (105). Both sets of positioning steps (10123) are provided with permanent magnet rings (106). A permanent magnet support seat (107) is sleeved on the permanent magnet ring (106). An annular gap is formed between the permanent magnet support seat (107) and the permanent magnet ring (106).

4. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 3, characterized in that: The permanent magnet ring (106) includes a first magnetic ring (1061) and a second magnetic ring (1062). The first magnetic ring (1061) is a split structure and is installed on the positioning step (10123) by bolts. Its outer wall is evenly provided with multiple sets of tenons (1063) along the circumferential direction. The second magnetic ring (1062) is an integral structure and its inner wall is evenly provided with multiple sets of tenons (1064) along the circumferential direction. The tenon (1064) is bolted to the mortise (1063).

5. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 4, characterized in that: The tenon (1064) is located away from the body of the second magnetic ring (1062) and is integrally formed with a wedge-shaped locking platform (10641) in the radial direction outward. Corresponding to the wedge-shaped mounting platform (10641), a matching wedge-shaped groove (10631) is provided on the mortise (1063), and the mating surfaces of the wedge-shaped mounting platform (10641) and the wedge-shaped groove (10631) are inclined at an angle of 15°-30°. The wedge-shaped card holder (10641) has a heat dissipation blade (10642) integrally formed on one side.

6. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 4, characterized in that: The permanent magnet support base (107) includes two sets of support rings (1071). The two sets of support rings (1071) are symmetrically arranged along the radial direction of the permanent magnet ring (106). A suspension cavity (201) is formed between the two sets of support rings (1071), and the second magnetic ring (1062) is located in the suspension cavity (201). Both sets of support rings (1071) are provided with support magnetic rings (1072) on the side near the positioning step (10123). The support magnetic rings (1072), the first magnetic ring (1061), and the second magnetic ring (1062) are all made of neodymium iron boron permanent magnet material. The mortise (1063) and the tenon (1064) are both made of titanium alloy. The magnetic poles on both sides of the support ring (1071) are aligned with the magnetic poles of the first magnetic ring (1061) and the second magnetic ring (1062) on opposite sides.

7. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 6, characterized in that: The magnetic field formed by the first magnetic ring (1061) and the magnetic field formed by the supporting magnetic ring (1072) generate an axial repulsive force, which is used to apply a reverse thrust toward the positioning step (10123) to the first magnetic ring (1061) to prevent the first magnetic ring (1061) from being dislodged from the installation position due to axial vibration during high-speed rotation; The magnetic field formed by the second magnetic ring (1062) and the magnetic field formed by the supporting magnetic ring (1072) generate a radial repulsive force, which is used to provide a radially inward constraint force for the second magnetic ring (1062), counteracting the radial expansion tendency of the second magnetic ring (1062) caused by centrifugal force, and helping to maintain the central position of the second magnetic ring (1062) in the suspension cavity (201).

8. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 7, characterized in that: The support ring (1071) is provided with multiple sets of magnetohydrodynamic damping rods (108) along the circumferential direction on the side away from the positioning step (10123). The magnetohydrodynamic damping rod (108) is provided with a magnetic sheet (109) on its movable rod, and a return spring (111) is sleeved on the magnetohydrodynamic damping rod (108).

9. A high-speed rotor assembly for a compressor that overcomes centrifugal force according to claim 8, characterized in that: The magnetic sheet (109) is L-shaped, and a U-shaped cavity (202) is formed between two adjacent sets of magnetic sheets (109). The second magnetic ring (1062) is located in the U-shaped cavity (202), and the magnetic poles of the opposite surfaces of the magnetic sheet (109) and the second magnetic ring (1062) are aligned. The repulsive force generated by the magnetic field formed by the magnetic sheet (109) and the magnetic field formed by the second magnetic ring (1062) is used to suppress the offset when the high-speed gear shaft (101) is offset.

10. A compressor, comprising a housing (301), characterized in that: The high-speed rotor assembly of the compressor according to any one of claims 1 to 9, which overcomes centrifugal force, is installed inside the housing (301).

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