CN106939931B - Radial hollow periodic structure gear hub with medium-low frequency vibration damping characteristic - Google Patents
Radial hollow periodic structure gear hub with medium-low frequency vibration damping characteristic Download PDFInfo
- Publication number
- CN106939931B CN106939931B CN201710279314.3A CN201710279314A CN106939931B CN 106939931 B CN106939931 B CN 106939931B CN 201710279314 A CN201710279314 A CN 201710279314A CN 106939931 B CN106939931 B CN 106939931B
- Authority
- CN
- China
- Prior art keywords
- wedge
- radial
- vibration
- solid rings
- solid
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000000737 periodic effect Effects 0.000 title claims abstract description 17
- 238000013016 damping Methods 0.000 title abstract description 11
- 239000007787 solid Substances 0.000 claims abstract description 45
- 230000005540 biological transmission Effects 0.000 abstract description 9
- 230000005284 excitation Effects 0.000 description 29
- 230000000694 effects Effects 0.000 description 6
- 238000004088 simulation Methods 0.000 description 6
- 239000000463 material Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 238000002474 experimental method Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000002955 isolation Methods 0.000 description 2
- 238000011089 mechanical engineering Methods 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000004458 analytical method Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005316 response function Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/14—Construction providing resilience or vibration-damping
Abstract
The invention relates to a gear hub with a radial hollowed-out periodic structure and a medium-low frequency vibration damping characteristic, which comprises a plurality of solid rings arranged from inside to outside, wherein wedge-shaped blocks are arranged between adjacent solid rings, the part, which is not connected with the wedge-shaped blocks, of the solid rings is in a hollowed-out structure, the wedge-shaped blocks from inside to outside rotate at a certain angle, and as the gear is in a transmission process, a shaft connected with the gear hub is subjected to vibration transmitted in the gear transmission process, and the vibration is continuously transmitted to the shaft and then transmitted to other parts of a machine to cause the machine to generate vibration.
Description
Technical Field
The invention relates to the technical field of anti-resonance vibration reduction, in particular to a radial hollowed-out periodic structure gear hub with medium-low frequency vibration reduction characteristics.
Background
Anti-resonance refers to the phenomenon that vibration is static in the whole system or some parts of the system under the excitation action of some specific frequencies in an elastic system. By reasonably designing the structural parameters of the system, the propagation of vibration can be suppressed in a certain frequency range. The anti-resonance theory has wide application prospect in the mechanical field.
In engineering machinery, the gears can generate vibration and noise with different degrees during high-speed operation, so that the service life of the gears can be reduced, noise pollution can be caused, and the physical health of staff is affected. Therefore, vibration reduction and noise reduction have important significance for improving the precision of mechanical equipment, prolonging the service life of the equipment and the like. At present, two main types of methods for reducing the vibration of gears exist, namely, the vibration is reduced, namely, the manufacturing and mounting precision of parts such as gears is improved; and secondly, the generated vibration is reduced by vibration isolation and other technologies. However, it is difficult to achieve a good vibration damping effect in the above technique, and vibration is inevitably generated in the gear during transmission.
Disclosure of Invention
In order to overcome the defects of the prior art, the invention aims to provide the radial hollow periodic structure gear hub with the middle-low frequency vibration damping characteristic, which has the vibration damping characteristic in a plurality of middle-low frequency bands for axial excitation, radial excitation and tangential excitation, and has the characteristics of simple structure and practicability.
In order to achieve the above purpose, the invention adopts the following technical scheme:
the utility model provides a radial fretwork periodic structure gear wheel hub with well low frequency damping characteristic, includes a plurality of solid rings 2 that set up from inside to outside, is provided with wedge 1 between adjacent solid rings 2, and the part that does not set up wedge 1 between the adjacent solid rings 2 is hollow structure, from inside to outside, and every layer of wedge 1 all is certain angle rotation relative to last layer.
The solid rings 2 are periodically arranged from inside to outside in the radial direction.
The central angle of the wedge-shaped block 1 is 18 degrees.
The solid ring 2 is five layers, and the wedge block 1 is four layers.
The number of wedge-shaped blocks 1 between every two adjacent solid rings 2 is four, and the wedge-shaped blocks are uniformly distributed.
The angles of sequential rotation of each layer of wedge blocks 1 which are uniformly distributed from inside to outside are 36 degrees, 36 degrees and 54 degrees clockwise respectively.
The outer diameter of the solid ring 2 at the outermost ring is 180mm, the inner diameter of the solid ring 2 at the innermost ring is 90mm, the radial hollowed-out distance between the adjacent solid rings 2 is 15mm, the radial width of the solid rings 2 is 15mm, the axial height of the solid rings 2 is 24mm, and the axial height of the wedge-shaped block 1 positioned at the axial height center of the solid rings 2 is 8mm.
The beneficial effects of the invention are as follows:
the radial hollowed-out periodic structure has the characteristic of vibration attenuation in a plurality of middle and low frequency bands for axial excitation, radial excitation and tangential excitation; the frequency band of vibration attenuation can be adjusted by adjusting the structural parameters of the solid ring and the wedge-shaped block. The gear hub with the radial hollowed-out periodic structure has potential application value in mechanical engineering, and can weaken the vibration of the gear in medium and low frequencies.
Drawings
Fig. 1 is a front view of the structure of the present invention.
Fig. 2 is a cross-sectional view of the structure of the present invention.
Fig. 3 is a simulation and experimental result of the axial vibration transmission of the present invention.
Fig. 4 is a simulation and experimental result of the radial vibration transmission of the present invention.
Fig. 5 is a simulation and experimental result of tangential vibration transmission according to the present invention.
Fig. 6 is a graph showing the effect of the axial height H of the solid ring of the present invention on the first vibration attenuation band of the structure under radial excitation.
Fig. 7 shows the effect of the axial height w of the wedge of the present invention on the first vibration attenuation band of the structure under radial excitation.
Fig. 8 is an illustration of the effect of the invention on the first vibration attenuation band of a structure under radial excitation when the specific gravity of the radial hollowed-out distance n and the radial width m of the solid ring is changed.
Detailed Description
The structural and operational principles of the present invention will be described in detail with reference to the accompanying drawings.
As shown in fig. 1 and 2, the gear hub with the radial hollowed-out periodic structure and the medium-low frequency vibration damping characteristic comprises a plurality of solid rings 2, wherein the solid rings 2 are periodically arranged from inside to outside in the radial direction, and adjacent solid rings 2 are connected by four wedge-shaped blocks 1. The four wedge blocks 1 are uniformly distributed in the circumferential direction, the central angle of each wedge block is 18 degrees, and the angles of sequential rotation of the wedge-shaped blocks 1 which are uniformly distributed from inside to outside in the radial direction are 36 degrees, 36 degrees and 54 degrees clockwise respectively.
In the invention, in order to enable the structure to have certain strength and rigidity, 45 steel is adopted as the material of the whole hollow disc structure, and specific material parameters are shown in table 1. Size parameters: the outer diameter of the outermost solid ring 2 is d=180 mm, the inner diameter of the innermost solid ring 2 is r=45 mm, the radial hollowed-out distance between adjacent solid rings 2 is n=15 mm, the radial width of the solid rings 2 is m=15 mm, the axial height of the solid rings 2 is H=24 mm, the axial height of the wedge-shaped blocks 1 positioned in the axial height center of the solid rings 2 is w=8 mm, the wedge-shaped blocks rotate from inside to outside by a certain angle a=36°, b=18°, and the central angle c=18° of each wedge-shaped block.
TABLE 1 Material parameters
| Material | Young's modulus | Poisson's ratio | Density of |
| No. 45 steel | 2.09e11Pa | 0.269 | 7890 |
The following two specific embodiments of the invention provide the vibration reduction characteristics of the radial hollowed-out periodic structure of the three-dimensional solid structure under the free boundary conditions in the middle-low frequency range under the axial excitation, the radial excitation and the tangential excitation; the influence of the structural parameters on the first vibration attenuation frequency band of the radial excitation is changed.
Example 1
Axial excitation, as shown in FIG. 3, has a very significant vibration attenuation region between 740-1397 Hz, 1681-1867 Hz, and 3258-3970 Hz. As can be seen from the figure, the comparison result of the simulation and the experiment is better, and the relative error of the natural frequency is not more than 10%, and the error belongs to an acceptable reasonable range in engineering application.
Radial excitation, as shown in fig. 4, has very good vibration damping effect especially in the frequency range of approximately 1500Hz between 409 and 1856Hz, and the vibration damping reaches more than-20 dB even in a large part of frequency range, so that the vibration is completely inhibited. The frequency of the peak value of the simulated and experimental frequency response function in the extraction diagram can obtain the relative error of not more than 5 percent and is within the reasonable range allowed by engineering.
The tangential excitation, as shown in fig. 5, is very good in the experiment and simulation results at the middle-high frequency, but in order to apply tangential pulse load to the structure conveniently in the middle-low frequency experiment, the structure is machined to have a diameter of 8mm, and is matched with a bolt, a fit gap exists between the bolt and a threaded hole, the impact of the fit gap on the middle-low frequency is large, the natural frequency is offset, and the frequency response of the structure measured by excitation is different from that calculated by a simulation model to a certain extent.
Example 2
By changing the axial height H of the thickness of the solid ring, as shown in FIG. 6, as the axial height of the solid ring of the radial hollowed-out periodic structure becomes larger, the lower boundary frequency of the first vibration attenuation frequency band of the structure is basically unchanged under radial excitation, but the frequency at the upper boundary moves towards low frequency, so that the first vibration attenuation frequency band of the structure becomes narrower.
Changing the axial height w of the wedge-shaped block, it can be seen from fig. 7 that as the axial height of the wedge-shaped block is continuously increased, the upper boundary of the first vibration attenuation frequency band of the structure is gradually increased under radial excitation, and then gradually becomes stable, and the bandwidth of vibration attenuation is nearly 400Hz more when the axial height is 20mm than when the axial height is 4mm, so that if the vibration attenuation of the structure to the middle and low frequency bands under radial excitation is only considered, the hollow connection part is obviously more beneficial.
When the radial hollowed-out distance n and the specific gravity of the radial width m of the solid ring are changed, as shown in fig. 8, as the m becomes larger and the n becomes smaller, the upper boundary of the first vibration attenuation frequency band of the structure moves to a high frequency and the lower boundary moves to a slightly low frequency under radial excitation, when the width of the hollowed-out part is very narrow, the structure has very excellent vibration isolation capability for radial excitation, and when m=25 mm and n=5 mm, the structure has vibration attenuation effect in the frequency band of 376Hz to 2323Hz which is approximately 2000 Hz.
It can be seen that with the structure of the present invention, it is possible to make:
the structure has excellent vibration damping characteristics at medium and low frequencies under axial excitation, radial excitation and tangential excitation.
And adjusting the first vibration attenuation frequency band of the structure under radial excitation by adjusting the structural parameters of the structure.
Therefore, the radial hollowed-out periodic structure can be applied to mechanical engineering and can weaken the vibration of the gear in medium and low frequencies.
The working principle of the invention is as follows:
the invention designs a novel radial hollowed-out periodic structure, which can be theoretically regarded as a hub part of a gear, is different from a solid disc structure of a traditional gear hub, and is periodically hollowed out in the radial direction, and four uniformly distributed wedge-shaped blocks 1 at hollowed-out parts connect two adjacent solid rings 2, and the four uniformly distributed wedge-shaped blocks 1 from inside to outside also rotate at a certain angle. Because the gear is in the in-process of transmission, the axle that is connected with gear wheel hub receives the vibration that the gear transmission in-process was transmitted, and the vibration is passed through constantly on the transmission axle and then is passed to other positions of machine again, causes the machine to produce the vibration. According to basic knowledge of vibration theory, for a multi-degree-of-freedom system, an anti-resonance frequency exists between two natural frequencies, and the anti-resonance refers to a phenomenon that vibration is static in the whole system or some parts of the system under the excitation action of some specific frequencies in an elastic system. If the analysis is made using the concept of mechanical impedance, the phenomenon of antiresonance, that is to say the situation where the system exhibits zero displacement admittance (dynamic compliance) at certain frequencies. As can be seen from the above frequency response curve of the radial hollowed-out periodic structure, the peak frequency of the frequency response curve of the radial hollowed-out periodic structure exactly corresponds to the natural frequency of the structure, and particularly for radial excitation, a significant vibration attenuation area exists in the frequency band between the formants, so that the vibration attenuation of low frequency in the radial hollowed-out periodic structure is caused by the antiresonance characteristic of the structure.
Claims (1)
1. The gear hub with the radial hollowed periodic structure and the medium-low frequency vibration reduction characteristic is characterized by comprising a plurality of solid rings (2) which are arranged from inside to outside, wedge-shaped blocks (1) are arranged between the adjacent solid rings (2), the part, which is not provided with the wedge-shaped blocks (1), between the adjacent solid rings (2) is in a hollowed structure, and each layer of wedge-shaped blocks (1) rotates at a certain angle relative to the upper layer from inside to outside;
the solid rings (2) are periodically arranged from inside to outside in the radial direction;
the central angles of the wedge blocks (1) are 18 degrees;
the solid ring (2) is five layers, and the wedge block (1) is four layers;
the number of wedge-shaped blocks (1) between every two adjacent solid rings (2) is four, and the wedge-shaped blocks are uniformly distributed;
the angles of sequential rotation of each layer of wedge blocks (1) which are uniformly distributed from inside to outside are respectively 36 degrees, 36 degrees and 54 degrees clockwise;
the outer diameter of the outermost solid ring (2) is 180mm, the inner diameter of the innermost solid ring (2) is 90mm, the radial hollowed-out distance between the adjacent solid rings (2) is 15mm, the radial width of the solid rings (2) is 15mm, the axial height of the solid rings (2) is 24mm, and the axial height of the wedge-shaped block (1) positioned in the axial height center of the solid rings (2) is 8mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710279314.3A CN106939931B (en) | 2017-04-25 | 2017-04-25 | Radial hollow periodic structure gear hub with medium-low frequency vibration damping characteristic |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710279314.3A CN106939931B (en) | 2017-04-25 | 2017-04-25 | Radial hollow periodic structure gear hub with medium-low frequency vibration damping characteristic |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106939931A CN106939931A (en) | 2017-07-11 |
| CN106939931B true CN106939931B (en) | 2024-02-02 |
Family
ID=59464756
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710279314.3A Active CN106939931B (en) | 2017-04-25 | 2017-04-25 | Radial hollow periodic structure gear hub with medium-low frequency vibration damping characteristic |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106939931B (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4825712A (en) * | 1984-07-20 | 1989-05-02 | Westinghouse Electric Corp. | Gear damping system |
| CN2083217U (en) * | 1990-12-25 | 1991-08-21 | 中国矿业大学 | Flexible wheel disc gear |
| CN101405524A (en) * | 2006-03-21 | 2009-04-08 | 罗伯特·博世有限公司 | Toothed wheel |
| CN103062362A (en) * | 2013-01-11 | 2013-04-24 | 哈尔滨工程大学 | Quasi-Bragg phonon crystal damping gear |
| CN203488596U (en) * | 2013-09-13 | 2014-03-19 | 重庆银钢科技（集团）有限公司 | Motorcycle clutch driven gear |
| CN105443724A (en) * | 2015-12-11 | 2016-03-30 | 湖南同晟精传技术有限公司 | Zero-backlash low-noise transmission gear |
| JP2016169852A (en) * | 2015-03-16 | 2016-09-23 | トヨタ自動車株式会社 | Torsional vibration reduction device |
| CN206738531U (en) * | 2017-04-25 | 2017-12-12 | 西安建筑科技大学 | A kind of radial direction hollow out periodic structure gear hub with middle low frequency vibration damping characteristic |
-
2017
- 2017-04-25 CN CN201710279314.3A patent/CN106939931B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4825712A (en) * | 1984-07-20 | 1989-05-02 | Westinghouse Electric Corp. | Gear damping system |
| CN2083217U (en) * | 1990-12-25 | 1991-08-21 | 中国矿业大学 | Flexible wheel disc gear |
| CN101405524A (en) * | 2006-03-21 | 2009-04-08 | 罗伯特·博世有限公司 | Toothed wheel |
| CN103062362A (en) * | 2013-01-11 | 2013-04-24 | 哈尔滨工程大学 | Quasi-Bragg phonon crystal damping gear |
| CN203488596U (en) * | 2013-09-13 | 2014-03-19 | 重庆银钢科技（集团）有限公司 | Motorcycle clutch driven gear |
| JP2016169852A (en) * | 2015-03-16 | 2016-09-23 | トヨタ自動車株式会社 | Torsional vibration reduction device |
| CN105443724A (en) * | 2015-12-11 | 2016-03-30 | 湖南同晟精传技术有限公司 | Zero-backlash low-noise transmission gear |
| CN206738531U (en) * | 2017-04-25 | 2017-12-12 | 西安建筑科技大学 | A kind of radial direction hollow out periodic structure gear hub with middle low frequency vibration damping characteristic |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106939931A (en) | 2017-07-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107542827A (en) | A kind of composite construction phonon crystal vibration isolating suspension | |
| CN106939931B (en) | Radial hollow periodic structure gear hub with medium-low frequency vibration damping characteristic | |
| CN103062362A (en) | Quasi-Bragg phonon crystal damping gear | |
| CN204200999U (en) | A kind of phonon crystal vibration-reduction gear | |
| CN106321775A (en) | Common low speed vibration-attenuating gear based on local resonance-type photonic crystals | |
| CN206738531U (en) | A kind of radial direction hollow out periodic structure gear hub with middle low frequency vibration damping characteristic | |
| CN204828549U (en) | Ordinary low -speed damping gear based on local resonance type phonon crystal | |
| US4542566A (en) | Corrugating roller | |
| CN111089117B (en) | Flexible vibration damping bearing bush | |
| CN207858627U (en) | A kind of durability grinding wheel of high-speed rotation | |
| CN204943688U (en) | Indoor apparatus of air conditioner and air-conditioner | |
| CN213206488U (en) | Vibration reduction gear and engine thereof | |
| CN105134629A (en) | Fan and air purifier | |
| CN108458087A (en) | A kind of lubricating type reducer gear that enhancing is stable | |
| CN104633048B (en) | Combined type radial profile-modified gear | |
| CN212617547U (en) | Pinch roller lubricating structure and vibration wheel thereof | |
| CN207246128U (en) | A kind of flabellum, wind turbine and air-conditioning | |
| CN211667120U (en) | Rubber vibration-damping noise-reducing gear | |
| CN204592138U (en) | Built-in wideband torsional vibration damper | |
| CN116379127A (en) | Tooth blank design method for vibration reduction and noise reduction and tooth blank | |
| DE102011115290A1 (en) | One-piece brake disk, has friction ring and pot-shaped carrier part rotationally symmetrically formed, where disk simultaneously has two types of eccentricities that have trochoid or waves of any order or polygons with rounded corners | |
| CN111255861A (en) | Planetary gear train with adjustable supporting rigidity and flexible damping vibration isolation gear ring | |
| CN201913500U (en) | Vibration attenuation device used in processing of intaglio roller | |
| CN209909114U (en) | Damping belt pulley | |
| CN105442275A (en) | Noise-reducing assembly and washing machine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |