Rotor structure for improving high speed dynamic balancing of flexible rotor
By setting counterweight holes in the rotor structure and performing dynamic balance calibration, the vibration problem of the flexible rotor at the critical speed was solved, high-precision dynamic balance of the rotor was achieved, and stable operation of the equipment was ensured.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SUZHOU LEGO MOTORS CO LTD
- Filing Date
- 2025-06-21
- Publication Date
- 2026-06-30
AI Technical Summary
Traditional dual-plane dynamic balancing methods cannot effectively handle the unbalanced mass of flexible rotors at different axial positions, resulting in severe vibrations at critical speeds, affecting normal equipment operation and causing rotor damage.
Multiple counterweight holes are set on the shaft, pressure plate and rotor core, and dynamic balance calibration is performed through counterweight components, including the design of threaded holes and rivet holes, to achieve batch processing and flexible calibration of rotor structure.
It effectively reduces the initial and residual imbalance of the rotor, improves the dynamic balancing accuracy, reduces the vibration amplitude, ensures stable operation of the rotor at the critical speed, and reduces the risk of equipment damage.
Smart Images
Figure CN224438613U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to the field of motor technology, specifically to a rotor structure for improving the high-speed dynamic balance of a flexible rotor. Background Technology
[0002] With the rapid development of industrial technology, the operating speeds of various industrial equipment, such as high-speed motors, aero engines, and precision machine tools, are constantly increasing, making the requirements for rotor dynamic balance accuracy increasingly stringent. The rotor dynamic balance state directly determines the stability, reliability, and service life of the equipment. Insufficient dynamic balance accuracy can lead to increased equipment vibration, increased noise, and even mechanical failures and safety accidents.
[0003] Currently, in the field of rotor dynamic balancing calibration, the dual-plane dynamic balancing method is widely used due to its advantages such as relatively simple operation and controllable cost. This method adjusts the rotor's imbalance by adding or adjusting counterweights at the pressure plates at both ends of the rotor, bringing the rotor's center of gravity as close as possible to the rotor's axis of rotation. For rigid rotors, this method can effectively improve their overall balance and ensure stable rotor vibration within the operating speed range, avoiding abrupt changes and bending deformation.
[0004] However, the aforementioned traditional two-plane dynamic balancing method has significant limitations. Firstly, it only focuses on the overall balance adjustment of the rotor. In reality, the unbalanced mass of a rigid rotor still exists in every axial section; the local imbalance is merely masked by counterweights at both ends. This can still potentially affect the performance of precision equipment with extremely high accuracy requirements. Secondly, the problem is even more pronounced for flexible rotors. When a flexible rotor operates near its critical speed, the vibration mode corresponding to that speed dominates the rotor deflection. The traditional two-plane dynamic balancing method cannot accurately handle the unbalanced mass distributed at different axial positions. At the critical speed, the interaction of these unbalanced masses can cause severe rotor vibration, leading to equipment malfunction or even rotor damage.
[0005] Therefore, how to overcome the shortcomings of the existing technology mentioned above has become the subject of this utility model. Utility Model Content
[0006] The purpose of this invention is to provide a rotor structure that improves the high-speed dynamic balance of a flexible rotor.
[0007] To achieve the above objectives, the technical solution adopted by this utility model is as follows:
[0008] A rotor structure for improving the high-speed dynamic balance of a flexible rotor, comprising:
[0009] Shaft;
[0010] Rotor cores are fixedly disposed on the outside of the rotating shaft and at least two are provided. Each rotor core is attached to the rotating shaft along the length direction of the rotating shaft and forms a core group.
[0011] Two pressure plates are fixedly disposed on the outside of the rotating shaft, with the two pressure plates disposed on both sides of the iron core assembly along the length direction of the rotating shaft.
[0012] The rotating shaft has multiple first counterweight holes at both ends along its length.
[0013] Each pressure plate is provided with multiple second counterweight holes;
[0014] Each rotor core is provided with multiple third counterweight holes;
[0015] The rotor structure also includes multiple counterweights corresponding to the first counterweight hole, the second counterweight hole and the third counterweight hole.
[0016] "Multiple" means at least two.
[0017] The counterweights are provided corresponding to the first counterweight hole, the second counterweight hole, and the third counterweight hole, and the number is not limited here.
[0018] Before assembling the rotor, the shaft, each rotor core and each pressure plate can be dynamically balanced. Taking the shaft as an example, by assembling the counterweight and the first counterweight hole, the dynamic imbalance of the shaft at the target speed can meet the design requirements. The same applies to each rotor core and each pressure plate.
[0019] Due to the setting of the first counterweight hole, the second counterweight hole, the third counterweight hole and the counterweight, the internal components can be dynamically balanced before the rotor is assembled to reduce the initial imbalance of the rotor. At the same time, the rotor as a whole can be dynamically balanced after the rotor is assembled to reduce the residual imbalance of the rotor and make its dynamic balance accuracy meet the design requirements, thereby effectively reducing the vibration amplitude of the rotor during operation.
[0020] In some embodiments, the first, second, and third counterweight holes are all located near the outer edge region of the corresponding structure. Taking the first counterweight hole as an example, the cross-section of the rotating shaft has an inner ring and an outer ring, and the first counterweight hole is located closer to the outer ring. In this case, the counterweight radius is larger, the mass required for counterweight is reduced, which is beneficial for dynamic balancing calibration.
[0021] The method of dynamic balancing is existing and can be achieved using existing devices such as dynamic balancing machines, which will not be elaborated here.
[0022] In a further technical solution, the first counterweight holes located at the same end of the rotating shaft are evenly distributed in a circular pattern around the axis of the rotating shaft.
[0023] With the design of this embodiment, on the one hand, the difficulty of opening the first counterweight hole can be reduced, which is suitable for batch processing of the rotating shaft; on the other hand, the rotating shaft can be flexibly calibrated according to the dynamic balance test results, thereby improving the dynamic balance calibration effect and further ensuring the rotor dynamic balance level (meeting expectations).
[0024] The dynamic balancing test results include the magnitude, phase, and axial position distribution of the imbalance.
[0025] In a further technical solution, the first counterweight hole is set as a first threaded hole;
[0026] The counterweight is partly configured as a first screw corresponding to the first threaded hole.
[0027] As mentioned above, by assembling the counterweight with the first counterweight hole, the dynamic imbalance of the shaft at the target speed can meet the design requirements. In this embodiment, the two are assembled by a threaded connection to ensure a stable connection, thereby avoiding the impact on the dynamic balance calibration effect of the shaft due to loosening or other issues, and further ensuring the dynamic balance level of the rotor.
[0028] A further technical solution is that the second counterweight holes on the same pressure plate are evenly distributed in a circular pattern around the axis of the pressure plate.
[0029] With the design of this embodiment, on the one hand, the difficulty of opening the second counterweight hole can be reduced, which is suitable for batch processing of the pressure plate; on the other hand, the pressure plate can be flexibly calibrated according to the dynamic balance test results, thereby improving the dynamic balance calibration effect and further ensuring the dynamic balance level of the rotor.
[0030] In a further technical solution, the second counterweight hole is configured as a second threaded hole;
[0031] The counterweight is partly configured as a second screw corresponding to the second threaded hole.
[0032] By assembling the counterweight with the second counterweight hole, the dynamic imbalance of the pressure plate at the target speed can meet the design requirements. In this embodiment, the two are assembled by threaded connection to ensure a stable connection, thereby avoiding the impact of loosening on the dynamic balance calibration effect of the pressure plate and further ensuring the dynamic balance level of the rotor.
[0033] A further technical solution is that the third counterweight holes on the same rotor core are evenly distributed in a circular pattern around the axis of the rotor core.
[0034] This section's design reduces the difficulty of creating the third counterweight hole, making it suitable for batch processing of rotor cores. Furthermore, it allows for flexible dynamic balancing of the rotor core based on dynamic balancing test results, improving the balancing effect and further ensuring the rotor's dynamic balance level.
[0035] In a further technical solution, the third counterweight hole is configured as a rivet hole;
[0036] Some of the counterweights are configured as rivets corresponding to the rivet holes.
[0037] Since each rotor core needs to be stacked to form a core assembly, and the pressure plate is located at both ends of the core assembly, this embodiment adopts rivet holes instead of threaded holes to reduce the processing difficulty of the rotor core, thereby reducing processing costs, and also preventing the counterweight from easily separating from the third counterweight hole.
[0038] In some embodiments, the third counterweight hole is a pin hole, and the corresponding counterweight is a pin.
[0039] In a further technical solution, the third counterweight hole is located in the middle region between the inner and outer rings of the rotor core.
[0040] It should be noted that the "intermediate area" does not necessarily refer to a specific area. For example, if the difference between the inner and outer diameters of the rotor core is set to 5 (units not considered), then the center of the third counterweight hole can be located in the area of 2-3.
[0041] By setting up this section, after opening the third counterweight hole, a certain thickness can be guaranteed in the areas on both sides of the third counterweight hole along the radial direction of the rotor core, reducing the risk of stress concentration and thus ensuring the structural strength of the rotor core.
[0042] The terms "first," "second," etc., used in this article do not specifically refer to order or sequence, nor are they intended to limit this case; they are merely used to distinguish components or operations described using the same technical terms.
[0043] The terms "connection" or "positioning" as used in this article can refer to two or more components or devices making direct physical contact with each other, or making indirect physical contact with each other, or to two or more components or devices operating or moving with each other.
[0044] The terms “include,” “including,” and “have” used in this article are all open-ended, meaning they include but are not limited to.
[0045] Unless otherwise specified, the terms used herein generally have their ordinary meaning in the context of the art, the subject matter, and the specific context. Certain terms used to describe this case will be discussed below or elsewhere in this specification to provide additional guidance to those skilled in the art in describing the case.
[0046] The terms “front,” “back,” “up,” “down,” “left,” and “right” used in this article are directional terms. In this case, they are only used to describe the positional relationship between the structures and are not intended to limit the specific direction of the protection scheme or its actual implementation.
[0047] The working principle and advantages of this utility model are as follows:
[0048] Before assembling the rotor, the shaft, each rotor core and each pressure plate can be dynamically balanced. Taking the shaft as an example, by assembling the counterweight and the first counterweight hole, the dynamic imbalance of the shaft at the target speed can meet the design requirements. The same applies to each rotor core and each pressure plate.
[0049] Due to the setting of the first counterweight hole, the second counterweight hole, the third counterweight hole and the counterweight, the internal components can be dynamically balanced before the rotor is assembled to reduce the initial imbalance of the rotor. At the same time, the rotor as a whole can be dynamically balanced after the rotor is assembled to reduce the residual imbalance of the rotor, so that its dynamic balance accuracy meets the design requirements and the imbalance mass distribution at each position of the rotor axis is effectively suppressed, thereby effectively reducing the vibration amplitude of the rotor during operation.
[0050] In summary, the rotor structure in this application is applicable to precision equipment with extremely high precision requirements, and at critical speeds, it can reduce the risk of rotor structure damage and equipment malfunction. Attached Figure Description
[0051] Figure 1 This is a schematic diagram of the rotor structure according to an embodiment of the present invention;
[0052] Figure 2 for Figure 1 A structural diagram from another perspective;
[0053] Figure 3 This is a schematic diagram of the structure of the rotating shaft in an embodiment of the present invention;
[0054] Figure 4 for Figure 3 A structural diagram from another perspective;
[0055] Figure 5 This is a schematic diagram of the structure of the non-magnetic steel rotor core according to an embodiment of the present invention;
[0056] Figure 6 This is a schematic diagram of the structure of the magnetic steel rotor core in an embodiment of the present invention.
[0057] In the above attached diagram: 1. Shaft; 2. Rotor core; 3. Pressure plate; 4. First counterweight hole; 5. Second counterweight hole; 6. Third counterweight hole. Detailed Implementation
[0058] The present invention will be further described below with reference to the accompanying drawings and embodiments:
[0059] Example: The present invention will be clearly described below with illustrations and detailed description. Any person skilled in the art who understands the examples of the present invention can make changes and modifications based on the technology taught in the present invention without departing from the spirit and scope of the present invention.
[0060] The terminology used herein is for the purpose of describing specific embodiments only and is not intended to limit the scope of this work. Singular forms such as “a,” “this,” “this,” “the,” and “the” as used herein also include plural forms.
[0061] See Figures 1-6 A rotor structure for improving the high-speed dynamic balance of a flexible rotor, comprising:
[0062] Shaft 1;
[0063] Rotor core 2 is fixedly disposed on the outside of the rotating shaft 1 and at least two are provided. Each rotor core 2 is attached to the rotating shaft 1 along the length direction of the rotating shaft 1 and forms a core group.
[0064] Two pressure plates 3 are fixedly disposed on the outside of the rotating shaft 1, with the two pressure plates 3 disposed on both sides of the iron core assembly along the length direction of the rotating shaft 1.
[0065] The rotating shaft 1 has multiple first counterweight holes 4 at both ends along its length.
[0066] Each pressure plate 3 is provided with multiple second counterweight holes 5;
[0067] Each rotor core 2 is provided with multiple third counterweight holes 6;
[0068] The rotor structure also includes multiple counterweights (not shown in the figure) corresponding to the first counterweight hole 4, the second counterweight hole 5 and the third counterweight hole 6.
[0069] "Multiple" means at least two.
[0070] The rotor core 2 may or may not have magnets; there are no restrictions here.
[0071] The counterweights are provided corresponding to the first counterweight hole 4, the second counterweight hole 5 and the third counterweight hole 6, and the number is not limited here.
[0072] Before assembling the rotor, the rotating shaft 1, each rotor core 2 and each pressure plate 3 can be dynamically balanced. Taking the rotating shaft 1 as an example, by assembling the counterweight and the first counterweight hole 4, the dynamic imbalance of the rotating shaft 1 at the target speed can meet the design requirements. The same applies to each rotor core 2 and each pressure plate 3.
[0073] Due to the arrangement of the first counterweight hole 4, the second counterweight hole 5, the third counterweight hole 6, and the counterweight components, dynamic balancing calibration can be performed on each internal component before rotor assembly to reduce the initial imbalance of the rotor. At the same time, dynamic balancing calibration can be performed on the entire rotor after assembly to reduce the residual imbalance of the rotor, ensuring that its dynamic balancing accuracy meets the design requirements. This also effectively suppresses the distribution of unbalanced mass at various axial positions of the rotor, thereby effectively reducing the vibration amplitude during rotor operation.
[0074] In some embodiments, the first counterweight hole 4, the second counterweight hole 5, and the third counterweight hole 6 are all located near the outer edge region of the corresponding structure. Taking the first counterweight hole 4 as an example, the cross-section of the rotating shaft 1 has an inner ring and an outer ring, and the first counterweight hole 4 is located closer to the outer ring. In this case, the counterweight radius is larger, the mass of the counterweight required is reduced, which is beneficial for dynamic balance calibration.
[0075] The method of dynamic balancing is existing and can be achieved using existing devices such as dynamic balancing machines, which will not be elaborated here.
[0076] See Figures 3-4 In this embodiment, each of the first counterweight holes 4 located at the same end of the rotating shaft 1 is uniformly distributed in a circular pattern around the axis of the rotating shaft 1.
[0077] With the configuration of this embodiment, on the one hand, the difficulty of opening the first counterweight hole 4 can be reduced, which is suitable for batch processing of the rotating shaft 1; on the other hand, the rotating shaft 1 can be flexibly calibrated according to the dynamic balance test results, thereby improving the dynamic balance calibration effect and further ensuring the rotor dynamic balance level (meeting expectations).
[0078] The dynamic balancing test results include the magnitude, phase, and axial position distribution of the imbalance.
[0079] In this embodiment, the first counterweight hole 4 is set as a first threaded hole;
[0080] The counterweight is partly configured as a first screw corresponding to the first threaded hole.
[0081] As mentioned above, by assembling the counterweight with the first counterweight hole 4, the dynamic imbalance of the rotating shaft 1 at the target speed can meet the design requirements. In this embodiment, the two are assembled by threaded connection to ensure a stable connection, thereby avoiding the impact on the dynamic balance calibration effect of the rotating shaft 1 due to loosening or other issues, and further ensuring the dynamic balance level of the rotor.
[0082] See Figures 1-2 In this embodiment, each of the second counterweight holes 5 on the same pressure plate 3 is uniformly distributed in a circular pattern around the axis of the pressure plate 3.
[0083] With the configuration of this embodiment, on the one hand, the difficulty of opening the second counterweight hole 5 can be reduced, which is suitable for batch processing of the pressure plate 3; on the other hand, the pressure plate 3 can be flexibly calibrated according to the dynamic balance test, thereby improving the dynamic balance calibration effect and further ensuring the dynamic balance level of the rotor.
[0084] In this embodiment, the second counterweight hole 5 is configured as a second threaded hole;
[0085] The counterweight is partly configured as a second screw corresponding to the second threaded hole.
[0086] By assembling the counterweight with the second counterweight hole 5, the dynamic imbalance of the pressure plate 3 at the target speed can meet the design requirements. In this embodiment, the two are assembled by threaded connection to ensure a stable connection, thereby avoiding the impact of loosening on the dynamic balance calibration effect of the pressure plate 3 and further ensuring the dynamic balance level of the rotor.
[0087] See Figures 5-6 In this embodiment, the third counterweight holes 6 on the same rotor core 2 are uniformly distributed in a circular pattern around the axis of the rotor core 2.
[0088] With the configuration of this embodiment, on the one hand, the difficulty of opening the third counterweight hole 6 can be reduced, which is suitable for the batch processing of rotor core 2; on the other hand, the rotor core 2 can be flexibly calibrated according to the dynamic balance test results, thereby improving the dynamic balance calibration effect and further ensuring the dynamic balance level of the rotor.
[0089] In this embodiment, the third counterweight hole 6 is set as a rivet hole;
[0090] Some of the counterweights are configured as rivets corresponding to the rivet holes.
[0091] Since each rotor core 2 needs to be stacked to form a core assembly, and the pressure plate 3 is located at both ends of the core assembly, this embodiment adopts rivet holes instead of threaded holes to reduce the processing difficulty of the rotor core 2, thereby reducing the processing cost, and also to prevent the counterweight from easily separating from the third counterweight hole 6.
[0092] In some embodiments, the third counterweight hole 6 is a pin hole, and the corresponding counterweight is a pin.
[0093] See Figures 5-6 In this embodiment, the third counterweight hole 6 is located in the middle region between the inner and outer rings of the rotor core 2.
[0094] It should be noted that the "intermediate region" does not necessarily refer to a specific value. For example, if the difference between the inner and outer diameters of the rotor core 2 is set to 5 (units not considered), then the center of the third counterweight hole 6 can be located in the region of 2-3.
[0095] With the configuration of this embodiment, after the third counterweight hole 6 is opened, the area on both sides of the rotor core 2 along the radial direction of the rotor core 2 can be guaranteed to have a certain thickness, reducing the risk of stress concentration and thus ensuring the structural strength of the rotor core 2.
[0096] The above embodiments are only for illustrating the technical concept and features of this utility model, and are intended to enable those skilled in the art to understand the content of this utility model and implement it accordingly. They should not be construed as limiting the scope of protection of this utility model. All equivalent changes or modifications made in accordance with the spirit and essence of this utility model should be included within the scope of protection of this utility model.
Claims
1. A rotor structure for improving the high-speed dynamic balance of a flexible rotor, characterized in that: include: Rotating shaft (1); Rotor cores (2) are fixedly disposed on the outside of the rotating shaft (1) and there are at least two of them. Each rotor core (2) is attached to the rotating shaft (1) along the length direction and forms a core group. Two pressure plates (3) are fixedly disposed on the outside of the rotating shaft (1), and the two pressure plates (3) are disposed on both sides of the iron core assembly along the length direction of the rotating shaft (1); The rotating shaft (1) has multiple first counterweight holes (4) at both ends along its length. Each pressure plate (3) is provided with multiple second counterweight holes (5); The rotor core (2) is provided with multiple third counterweight holes (6). The rotor structure also includes multiple counterweights corresponding to the first counterweight hole (4), the second counterweight hole (5) and the third counterweight hole (6).
2. The rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 1, characterized in that: The first counterweight holes (4) located at the same end of the rotating shaft (1) are evenly distributed in a circular pattern around the axis of the rotating shaft (1).
3. The rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 2, characterized in that: The first counterweight hole (4) is set as the first threaded hole; The counterweight is partly configured as a first screw corresponding to the first threaded hole.
4. The rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 1, characterized in that: The second counterweight holes (5) on the same pressure plate (3) are evenly distributed in a circular pattern around the axis of the pressure plate (3).
5. The rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 4, characterized in that: The second counterweight hole (5) is set as the second threaded hole; The counterweight is partly configured as a second screw corresponding to the second threaded hole.
6. The rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 1, characterized in that: The third counterweight holes (6) on the same rotor core (2) are evenly distributed in a circular pattern around the axis of the rotor core (2).
7. A rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 6, characterized in that: The third counterweight hole (6) is set as a rivet hole; Some of the counterweights are configured as rivets corresponding to the rivet holes.
8. A rotor structure for improving the high-speed dynamic balance of a flexible rotor according to claim 6, characterized in that: The third counterweight hole (6) is located in the middle area between the inner and outer rings of the rotor core (2).