Vibration reduction gear capable of adjusting multiple resonance points and design method of vibration reduction gear

Abstract

The invention discloses an adjustable multi-resonance-point vibration reduction gear and a design method thereof, and relates to the technical field of mechanical transmission gears. The problems that related vibration attenuation measures are adopted for a vibration source and a transmission path in most gear structures obtained through an existing gear transmission device vibration and noise reduction method, and multi-frequency-band vibration such as gear rotating frequency and meshing frequency cannot be attenuated are solved. According to the gear vibration reduction method, the detachable damping resonance blocks are arranged on the spoke of the gear in the radial array mode, vibration reduction can be conducted on multiple frequencies such as rotating frequency and meshing frequency at the same time, and the vibration reduction effect is good; the detachable damping resonance block is simple in design, simple in processing technology and good in installation manufacturability; in addition, the actual vibration reduction effect and the theoretical design deviation can be rapidly corrected by independently adjusting the damping resonance block which is detached and installed, and it is found through simulation analysis that the vibration displacement of the gear spoke of the gear body can be reduced by 15%-30% within multiple frequency bands such as the rotating frequency and the meshing frequency. The method is suitable for the technical field of vibration reduction gear structure design.

Description

Technical Field

[0001] This invention relates to the field of mechanical transmission gear technology, specifically to an adjustable multi-resonance point vibration damping gear and its design method. Background Technology

[0002] Gear transmission is a common form of transmission widely used in various mechanical equipment. Its main advantages include high transmission efficiency, compact structure, precise transmission, long service life, and high reliability. However, gear transmission also suffers from vibration problems such as meshing excitation, spoke resonance, and torsional vibration. This is especially true for high-speed gear transmissions, which require detailed optimization of tooth profile parameters and spoke structure. In applications with high requirements for vibration and noise reduction, special vibration reduction designs are even necessary.

[0003] Currently, most common vibration reduction and noise reduction methods for gear transmission devices involve taking relevant vibration attenuation measures targeting the vibration source and transmission path. For example, gear profile modification design technology reduces vibration noise from the direction of the vibration source; setting vibration damping structures on gear spokes, gear shaft support bearings, and housings reduces noise from the direction of the transmission path. For gear transmissions with high requirements for vibration reduction and noise reduction, improving machining accuracy and optimizing gear profile design to take into account factors such as load and temperature have become indispensable vibration reduction and noise reduction design methods. Currently, many scholars are also further reducing gear transmission noise through vibration reduction and noise reduction design of the transmission path of the gear transmission. Common design methods include: setting damping rings on the gear spoke body for vibration reduction; using extruded oil film structures on the gear shaft support bearings to attenuate vibration; and implementing relevant vibration isolation designs on the gear support housing. The basic principle of various design methods is to attenuate the vibration energy transmitted from the vibration source at the gear meshing point. In engineering, multiple vibration reduction measures are often used in combination to achieve higher vibration performance. However, since each vibration reduction design has a certain range of applicability, and often a single vibration reduction design can only effectively reduce vibration within a certain bandwidth, such as setting a damping ring on the gear spoke body, it often only attenuates a specific meshing frequency that resonates with the natural frequency of the gear spoke; the use of a squeezed oil film structure on the support bearing often only attenuates the transverse vibration of the gear shaft at rotational frequency; and the above designs are often complex in design and manufacturing processes, making it difficult to adjust the processability to correct the deviation between the actual vibration reduction situation and the theoretical calculation.

[0004] In summary, most existing methods for vibration reduction and noise reduction in gear transmission devices only address vibration attenuation measures for the vibration source and transmission path, failing to address the issue of attenuating vibrations across multiple frequency bands, such as gear rotation frequency and meshing frequency. Summary of the Invention

[0005] This invention addresses the problem that existing methods for vibration reduction and noise reduction in gear transmission devices mostly focus on vibration attenuation measures for the vibration source and transmission path, failing to attenuate vibrations across multiple frequency bands such as gear rotation frequency and meshing frequency. Therefore, this invention proposes an adjustable multi-resonance point vibration-damping gear and its design method.

[0006] The present invention provides an adjustable multi-resonance point vibration damping gear, which comprises a gear body 10 and a damping resonant block 20.

[0007] A damping resonant block 20 is provided at the center of the spokes 12 on the gear body 10; the damping resonant block 20 includes a connecting arc plate 21, a stiffness support beam 22 and a cylindrical damping block 23. The stiffness support beam 22 is provided on the outer circumference of the cylindrical damping block 23, and the connecting arc plate 21 is provided at the top of the stiffness support beam 22. The connecting arc plate 21 on the damping resonant block 20 is connected to the outer surface of the mounting hub 13 on the gear body 10 by a pin.

[0008] Furthermore, the curvature of the connecting arc-shaped piece 21 on the damping resonator block 20 is the same as the curvature of the outer surface of the mounting hub 13 on the gear body 10.

[0009] Furthermore, the connecting arc-shaped plate 21, the stiffness support beam 22, and the cylindrical damping block 23 are integrally formed;

[0010] A design method for an adjustable multi-resonance point vibration damping gear is described below:

[0011] Step S10: Begin the design task of the adjustable multi-resonance point vibration damping gear, which includes understanding the operating conditions of the gear body 10, such as speed and load, and collecting relevant geometric parameters of the gear.

[0012] Step S20: Model the gear using relevant numerical simulation software;

[0013] Step S30: Set material and constraint conditions for the gear model and perform modal analysis calculations;

[0014] Step S40: Based on modal simulation, set the rotational speed and load under actual working conditions, and perform structural harmonic response analysis and calculation using numerical simulation software;

[0015] Step S50: Analyze and confirm the target frequency and mode shape that require vibration reduction design within the operating frequency range;

[0016] Step S60: Based on the analysis results and vibration reduction design objectives, match and design the damping resonator block 20, and perform the optimized calculations again according to steps S30, S40, and S50.

[0017] Step S70: Analyze the vibration reduction effect. If the design target is met, proceed to step S80 to complete the gear design task with adjustable multi-resonance points. If the design target is not met, proceed to step S60 to optimize and match the design of the damping resonator block 20. Then, repeat the optimization calculations according to steps S30, S40, and S50 until the design target is met. Proceed to step S80 to complete the gear design task with adjustable multi-resonance points.

[0018] Furthermore, the relevant geometric parameters of the gear body 10 in step S10 include the number n and diameter d of the weight-reducing holes distributed at intervals φ° on the pitch circle of the diameter D of the spokes 12, as well as the material of the gear body 10.

[0019] Furthermore, in step S60, the matching design of the damping resonator block 20 mainly involves matching the width B, thickness A, and height H of the stiffness support beam 22 in the damping resonator block 20, and further designing the diameter D and length L of the cylindrical damping block 23 in the damping resonator block 20.

[0020] Compared with the prior art, the present invention has the following advantages:

[0021] This invention overcomes the shortcomings of existing technologies. The vibration-damping gear method of this invention, by radially arraying detachable damping resonator blocks on the gear spokes, can simultaneously reduce vibration at multiple frequencies, including rotational frequency and meshing frequency, resulting in excellent vibration reduction. The detachable damping resonator blocks are simple in design, easy to manufacture, and easy to install. Furthermore, by individually adjusting the detachable and installed damping resonator blocks, the deviation between the actual vibration reduction effect and the theoretical design can be quickly corrected. Based on simulation calculations, an example of a vibration-damping gear with adjustable multi-resonance points designed according to this invention, compared to a gear design method without vibration reduction, shows through simulation analysis that the vibration displacement of the gear body and gear spokes can be reduced by 15-30% across multiple frequency bands, including rotational frequency and meshing frequency. Attached Figure Description

[0022] Figure 1 This is a three-dimensional structural schematic diagram of an adjustable multi-resonance point vibration damping gear according to the present invention;

[0023] Figure 2 This is a top view of an adjustable multi-resonance point vibration damping gear according to the present invention;

[0024] Figure 3 This is a side sectional view of an adjustable multi-resonance point vibration damping gear AA as described in this invention;

[0025] Figure 4 This is a three-dimensional structural diagram of a damping resonator block in an adjustable multi-resonance point vibration-damping gear according to the present invention.

[0026] Figure 5This is a flowchart of a design scheme for an adjustable multi-resonance point vibration damping gear according to the present invention;

[0027] Figure 6 This is a comparison diagram of the simulation calculation modal results of the original structure of the adjustable multi-resonance point vibration-damping gear described in this invention at the target frequency order;

[0028] Figure 7 This is a simulation view of the amplitude sweep frequency harmonic response at the edge of an existing vibration damping gear under a 100N meshing force excitation.

[0029] Figure 8 This is a simulation view of the amplitude sweep frequency harmonic response at the edge of an adjustable multi-resonance point damping gear described in this invention under a 100N meshing force excitation.

[0030] Figure 9 yes Figure 7 and Figure 8 Comparison chart of simulation calculation results;

[0031] This includes a gear body 10, a damping resonator block 20, a tooth 11, a spoke 12, a mounting hub 13, a connecting arc plate 21, a stiffness support beam 22, and a cylindrical damping block 23. Detailed Implementation

[0032] Specific implementation method one: Combining Figures 1 to 4 This embodiment describes an adjustable multi-resonance point damping gear, which comprises a gear body 10 and a damping resonant block 20.

[0033] A damping resonant block 20 is provided at the center of the spokes 12 on the gear body 10. The damping resonant block 20 includes a connecting arc plate 21, a stiffness support beam 22 and a cylindrical damping block 23. The stiffness support beam 22 is provided on the outer circumference of the cylindrical damping block 23. The top of the stiffness support beam 22 is provided with a connecting arc plate 21. The connecting arc plate 21 on the damping resonant block 20 is connected to the outer surface of the mounting hub 13 on the gear body 10 by a pin.

[0034] Specific Implementation Method Two: Combining Figures 1 to 4 This embodiment further defines the damping gear described in Specific Embodiment 1. In this embodiment, the curvature of the connecting arc plate 21 on the damping resonant block 20 is the same as the curvature of the outer surface of the mounting hub 13 on the gear body 10.

[0035] Specific implementation method three: Combining Figures 1 to 4This embodiment further defines the damping gear described in Specific Embodiment 1. In this embodiment, the adjustable multi-resonance point damping gear is provided in which the connecting arc plate 21, the stiffness support beam 22, and the cylindrical damping block 23 are integrally formed.

[0036] Specific implementation method four: Combination Figures 1 to 9 This embodiment describes a design method for an adjustable multi-resonance point vibration damping gear, the specific design method of which is as follows:

[0037] Step S10: Begin the design task of the adjustable multi-resonance point vibration damping gear, which includes understanding the operating conditions of the gear body 10, such as speed and load, and collecting relevant geometric parameters of the gear.

[0038] Step S20: Model the gear using relevant numerical simulation software;

[0039] Step S30: Set material and constraint conditions for the gear model and perform modal analysis calculations;

[0040] Step S40: Based on modal simulation, set the rotational speed and load under actual working conditions, and perform structural harmonic response analysis and calculation using numerical simulation software;

[0041] Step S50: Analyze and confirm the target frequency and mode shape that require vibration reduction design within the operating frequency range;

[0042] Step S60: Based on the analysis results and vibration reduction design objectives, match and design the damping resonator block 20, and perform the optimized calculations again according to steps S30, S40, and S50.

[0043] Step S70: Analyze the vibration reduction effect. If the design target is met, proceed to step S80 to complete the gear design task with adjustable multi-resonance points. If the design target is not met, proceed to step S60 to optimize and match the design of the damping resonator block 20. Then, repeat the optimization calculations according to steps S30, S40, and S50 until the design target is met. Proceed to step S80 to complete the gear design task with adjustable multi-resonance points.

[0044] This specific embodiment, combined with common parallel shaft gear examples, details the process and beneficial results of the present invention. Figure 2As can be seen, the gear body 10 is a common parallel shaft gear with n weight-reducing holes of diameter d evenly distributed at intervals φ° on the pitch circle of the spokes 12 with diameter D. The material and specific structure of the gear body 10, such as the pitch circle diameter D and the distribution pattern n×φ°, determine the natural frequency and mode shape of the original gear. The mode shape and frequency of the original gear can be calculated through steps S10 to S50. Through the analysis of gear rotation frequency, meshing frequency, etc., it is confirmed that the mode shape and frequency of the first order 2319HZ and the third order 3980Hz need to be designed for vibration reduction, with the goal of reducing the amplitude at the edge of the gear by more than 10%. Next, the damping resonator 20 is designed to match the target frequency. Specifically, this is achieved through the design of the stiffness support beam 22 and the cylindrical damping block 23 to obtain the specific substructure resonance frequency and mode shape. The general principle is that the natural frequency of the damping resonator 20 should be close to the target vibration reduction frequency, and its mode shape should be the same as the mode shape of the target vibration reduction frequency in the principal direction. In this way, by matching the specific vibration mode of the gear body 10, the damping resonator 20 will generate a phase coupling effect with the gear body 10. The damping resonator 20 absorbs a portion of the vibration energy from the gear body 10 and converts it into heat energy through the damping effect of the damping resonator 20. In order to obtain the target frequency and mode shape during the initial matching design, the geometric parameters of the stiffness support beam 22 and the cylindrical damping block 23 of the damping resonator 20 can be adjusted. In this example, the width B, thickness A, and height H of the cross section of the stiffness support beam 22 and the diameter D and length L of the cylindrical damping block 23 can be adjusted.

[0045] After vibration reduction design, modal and harmonic response analysis was performed on the new structure according to steps S30 to S40. Through iterative design, the modal calculation results obtained for this example are as follows. Figure 6 It can be seen that the damping resonator 20 participates in the vibration mode motion of the gear body 10 at the target frequency. Following step S60, based on modal simulation, the amplitude sweep frequency harmonic response at the gear edge under a 100N meshing force excitation is analyzed, and the results are obtained. Figure 7 and Figure 8 The harmonic response curve will Figure 7 and Figure 8 Putting the amplitude curves together, for example Figure 9 As shown, it can be seen that near the first and third orders, the natural frequency is adjusted due to the introduction of the damping resonator. At the same time, under the same excitation amplitude, the amplitude of the first order vibration decreases from 0.033mm to 0.023mm, a decrease of 30.3%; the amplitude of the third order vibration decreases from 0.0132mm to 0.0106mm, a decrease of 19.6%.

[0046] In summary, this invention utilizes a radial array of detachable damping resonators mounted on the gear spokes. The natural frequencies of these resonators are designed to match common vibration frequencies such as gear rotation frequency and meshing frequency. When the gear vibrates at these frequencies, the damping resonators vibrate accordingly. By matching the specific vibration modes of the gear body, the damping resonators achieve phase coupling with the gear body. This allows the damping resonators to absorb some vibration energy from the main structure and convert it into heat energy through their damping effect, thereby reducing the vibration of the gear body. Simulation calculations show that the gear design based on this method reduces the vibration displacement of the gear spokes by 15-30% across multiple frequency bands, including rotation frequency and meshing frequency.

[0047] Specific Implementation Method Five: Combining Figures 1 to 9 This embodiment further defines the design method described in Specific Embodiment Four. The design method of an adjustable multi-resonance point damping gear described in this embodiment includes the following geometric parameters of the gear body 10 in step S10: the number n and diameter d of the weight reduction holes distributed at intervals φ° on the pitch circle of the diameter D of the spokes 12, and the material of the gear body 10.

[0048] Specific Implementation Method Six: Combination Figures 1 to 9 This embodiment further defines the design method described in Specific Embodiment Four. In this embodiment, the design method for an adjustable multi-resonance point damping gear involves matching the design of the damping resonator block 20 in step S60. This mainly involves matching the width B, thickness A, and height H of the stiffness support beam 22 in the damping resonator block 20, and further designing the diameter D and length L of the cylindrical damping block 23 in the damping resonator block 20.

Claims

1. A vibration-reducing gear with adjustable multiple resonance points, characterized in that: It comprises a gear body (10) and a damping resonance block (20); A damping resonance block (20) is provided at the center of the spoke (12) on the gear body (10); the damping resonance block (20) comprises a connecting arc piece (21), a rigidity support beam (22) and a cylindrical damping block (23); a rigidity support beam (22) is provided on the circumferential outer surface of the cylindrical damping block (23); a connecting arc piece (21) is provided at the top end of the rigidity support beam (22); and the connecting arc piece (21) on the damping resonance block (20) is connected to the outer surface of the mounting hub (13) on the gear body (10) via a pin.

2. The vibration-damping gear with adjustable multiple resonance points according to claim 1, characterized in that: The curvature of the connecting arc-shaped piece (21) on the damping resonance block (20) is the same as the curvature of the outer surface of the mounting hub (13) on the gear body (10).

3. The vibration-damping gear with adjustable multiple resonance points according to claim 1, characterized in that: The connecting arc piece (21), the rigidity support beam (22) and the cylindrical damping block (23) are integrally arranged.

4. The design method of a vibration-damping gear with adjustable multiple resonance points according to any one of claims 1 to 3, characterized in that: The specific design method is as follows: Step S10: starting the design task of the adjustable multi-resonance point vibration-damping gear, which includes understanding the use conditions of the gear body (10), such as rotation speed, load, etc., and collecting relevant geometric parameters of the gear; Step S20: Modeling the gear using relevant numerical simulation software; Step S30: setting material, constraint and other conditions for the gear model and performing modal analysis calculation; Step S40: on the basis of modal simulation, setting the speed and load of the actual working condition, and performing structural harmonic response analysis and calculation in combination with numerical simulation software; Step S50: analyzing and confirming the target frequency that needs vibration reduction design and the vibration mode that needs to be optimized in the operating frequency range; Step S60: Combine the analysis results and the vibration reduction design objectives, match and design the damping resonance block (20), and perform the optimized calculation again according to steps S30, S40, and S50: Step S70: Analyze the vibration reduction effect. If the design target is met, go to step S80 to complete the gear design task with adjustable multiple resonance points. If the design target is not met, go to step S60 to optimize the matching and design of the damping resonance block (20); The optimized calculations are repeated in a cycle according to steps S30, S40, and S50 until the design target is met, and then the process goes to step S80 to complete the gear design task with adjustable multiple resonance points.

5. The design method of a vibration-damping gear with adjustable multiple resonance points according to claim 4 is characterized in that: The geometric parameters related to the gear body (10) in step S10 include the number n and diameter d of the weight-reducing holes distributed at intervals of φ° on the pitch circle of the spoke (12) diameter D, and the material of the gear body (10).

6. The design method of a vibration-damping gear with adjustable multiple resonance points according to claim 4 is characterized in that: In the step S60, the damping resonance block (20) is matched and designed, mainly the width B, thickness A and height H of the rigidity support beam (22) in the damping resonance block (20) are matched and designed, and the diameter D and length L of the cylindrical damping block (23) in the damping resonance block (20) are designed.

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