CN116043641A - Multi-frequency superposition vibration steel wheel and vibratory roller - Google Patents
Multi-frequency superposition vibration steel wheel and vibratory roller Download PDFInfo
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- CN116043641A CN116043641A CN202310092353.8A CN202310092353A CN116043641A CN 116043641 A CN116043641 A CN 116043641A CN 202310092353 A CN202310092353 A CN 202310092353A CN 116043641 A CN116043641 A CN 116043641A
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
- E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
- E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
- E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
- E01C19/285—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows with attachments for work other than rolling, e.g. dozer blades, shoes for conversion into plate vibrator; fitted to vehicles, road-construction or earth-moving machinery ; vibrated or the like auxiliary rolls, e.g. for rolling road edges; provided with means for facilitating transport
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
- E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
- E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
- E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
- E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll
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- Engineering & Computer Science (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
- Road Paving Machines (AREA)
Abstract
The invention discloses a multi-frequency superposition vibration steel wheel and a vibration road roller, wherein the steel wheel comprises a wheel body, a main vibration excitation device and an auxiliary vibration excitation device; the main vibration excitation device is arranged at the geometric center position inside the wheel body through a vibration bearing and a radial plate and comprises a main vibration excitation shaft and a main vibration excitation eccentric block; the auxiliary vibration excitation device is arranged in bilateral symmetry relative to the main vibration excitation device, the auxiliary vibration excitation device comprises an auxiliary vibration excitation shaft and auxiliary vibration excitation eccentric blocks, and the synthetic eccentricity of all the auxiliary vibration excitation eccentric blocks is 15% -40% of the eccentricity of the main vibration excitation eccentric blocks; when the vibration device is in a working state, the auxiliary vibration shafts and the main vibration shafts rotate in the same direction, the rotating speeds of all the auxiliary vibration shafts are the same, and the rotating speed of the auxiliary vibration shafts is 2 times or 3 times or 4 times that of the main vibration shafts. The multi-frequency superposition vibration steel wheel can output special regular double-frequency vibration, can improve rolling speed and compaction efficiency, and can ensure stability of a compaction process and uniformity of soil after compaction.
Description
Technical Field
The invention relates to a steel wheel of a vibratory roller and the vibratory roller, in particular to a multi-frequency superposition vibratory steel wheel and the vibratory roller, and belongs to the technical field of vibratory rollers.
Background
The vibratory roller is engineering machinery for compacting various building and road construction materials by utilizing the gravity and vibration of the vibratory roller, and the vibration load emitted by the vibratory roller can enable the particles of the compacted soil (such as earth and stone filling, pavement paving mixture and the like) to be in a high-frequency vibration state so as to lose the internal friction among the particles, and further force the particles to be rearranged in a compacting way, so that higher compaction efficiency and better compaction effect can be obtained, and the vibratory roller is widely applied to compacting various non-cohesive soil, broken stone mixture and various asphalt concrete.
The vibrating wheel is one of key components of the vibratory roller, and is a working device of the vibratory roller and a traveling device of the vibratory roller. The vibrating wheel generally rotates around the axis of the inner rim assembly of the vibrating wheel to realize the walking function of the vibratory roller, and meanwhile, periodic exciting force is usually generated through high-speed rotation of a vibration exciter assembled inside the vibrating wheel, so that the part inside the vibration absorber of the vibrating wheel continuously generates mechanical vibration, and vibration and compaction of the compacted soil particles are forced.
In general, a process is needed for changing soil particles from a static initial state to a moving state, and experiments show that in order to overcome cohesive force and adsorption force among the particles, the general loam should be subjected to forced vibration for at least three times to enable the soil particles to be in a vibrating state, so that after the vibration frequency is determined under the condition that the curvature radius of a vibrating steel wheel (namely, the parameter affecting the grounding area of the vibrating steel wheel) is a certain value, the maximum rolling speed of the vibrating road roller is correspondingly determined. On the other hand, to ensure that the soil is uniformly compacted, it is necessary to ensure that the compaction work obtained by compacting the soil per unit length is equal, which requires that the compactor travel at a steady compaction speed (to ensure that the length of travel of the compactor per unit time is equal) and vibrate at a steady vibration frequency (to ensure that the work output by the compactor per unit time is equal).
The existing circumferential vibration, vertical vibration and other vibration modes in the industry all adopt single-frequency vibration with a certain proportion relation with the natural frequency of the compacted soil particles, so that the vibration wheel of the road roller can only vibrate with the same single frequency as the vibration frequency under the normal compaction working condition (non-jump working condition) after vibration starting is completed, and at the moment, the maximum rolling speed of the vibratory roller is limited by the vibration frequency with a certain proportion relation with the natural frequency. For example, single steel wheel rollers are typically excited at 33Hz and the vibration wheel outputs at 33Hz at normal compaction (non-skip), and vibratory roller compaction speeds are typically not recommended to exceed 6km/h.
The chaotic vibration concept of nonlinear vibration is also proposed in the industry, irregular vibration is output under deterministic input, multiple vibration frequencies can be output, the frequency band is wider, a certain vibration frequency can be selected to match and improve the compaction speed theoretically, however, the output of a chaotic vibration mode is uncontrollable, and the soil compaction is possibly uneven.
Therefore, how to realize the vibration wheel of the vibratory roller to vibrate at a plurality of vibration frequencies and determine and improve the rolling speed according to the highest vibration frequency so as to improve the compaction efficiency, and how to realize the periodic vibration of the vibration wheel with stable and regular output under deterministic input so as to ensure the uniformity of the compacted soil are the problems needed to be solved by the technicians in the field.
Disclosure of Invention
Aiming at the problems in the prior art, the invention provides the multi-frequency superposition vibration steel wheel and the vibratory roller, which can realize regular multi-frequency periodic vibration, and can realize the improvement of rolling speed and compaction efficiency on the premise of ensuring the uniformity of the compacted soil.
In order to achieve the purpose, the multi-frequency superposition vibration steel wheel comprises a wheel body, a main vibration excitation device and an auxiliary vibration excitation device;
the wheel body comprises a rim with a cylindrical structure and a plurality of layers of radial plates which are coaxially and fixedly arranged in the rim and are symmetrically arranged relative to the rim left and right along the axial direction, and the radial plates at the outermost layer of the wheel body are used for connecting the steel wheel with a frame or a driving plate of the vibratory roller through a shock absorber;
the main vibration excitation device is arranged at the geometric center position inside the wheel body through a vibration bearing and a radial plate, and comprises a main vibration excitation shaft coaxially arranged with the wheel body and a main vibration excitation eccentric block fixedly arranged on the main vibration excitation shaft and extending out along the radial direction of the main vibration excitation shaft, and a main vibration excitation driving mechanism is arranged on the main vibration excitation shaft;
the auxiliary vibration device is arranged in bilateral symmetry relative to the main vibration device, the auxiliary vibration device comprises an auxiliary vibration shaft which is coaxially arranged with the wheel body and auxiliary vibration eccentric blocks which are fixedly arranged on the auxiliary vibration shaft and extend out along the radial direction of the auxiliary vibration shaft, an auxiliary vibration driving mechanism is arranged on the auxiliary vibration shaft, and the synthetic eccentric distance of all the auxiliary vibration eccentric blocks is 15% -40% of the eccentric distance of the main vibration eccentric blocks;
when the vibration device is in a working state, the auxiliary vibration shafts and the main vibration shafts rotate in the same direction, the rotating speeds of all the auxiliary vibration shafts are the same, and the rotating speed of the auxiliary vibration shafts is 2 times or 3 times or 4 times that of the main vibration shafts.
As one embodiment of the present invention, the initial phase difference between the secondary excitation eccentric mass and the primary excitation eccentric mass is 0 °.
As another embodiment of the present invention, the initial phase difference between the secondary excitation eccentric mass and the primary excitation eccentric mass is 90 °.
As a further improvement scheme of the invention, the main excitation driving mechanism and the auxiliary excitation driving mechanism share the same excitation driving mechanism, and the auxiliary excitation vibrating shaft is in transmission connection with the main excitation vibrating shaft.
As a preferable mode of the present invention, the main excitation driving mechanism and the sub-excitation driving mechanism share the same main excitation driving mechanism.
As one embodiment of the present invention, the secondary excitation vibration shaft and the primary excitation vibration shaft are connected by a gear transmission.
A vibratory roller includes a multi-frequency stacked vibratory steel wheel.
Compared with the prior art, the multi-frequency superposition vibration steel wheel can superpose and output special regular double-frequency vibration through frequency, amplitude and phase combination, the basic frequency which has a certain proportion relation with the natural frequency of the compacted soil particles can drive the soil particles to move, the stability of the compaction process and the uniformity of the compacted soil can be ensured, the high frequency which has a multiple relation with the basic frequency can drive the soil particles to realize forced vibration for a plurality of times to be in a vibration state, the rolling speed and the compaction efficiency can be improved, and the special, stable and regular multi-frequency superposition output is adopted, so that the downward vibration amplitude can be effectively increased when the initial phase difference of the auxiliary vibration eccentric block and the main vibration eccentric block is 0 degree, the ground acting force of the steel wheel can be increased, the compaction efficiency can be improved, the upward amplitude of the steel wheel can be effectively reduced when the initial phase difference of the auxiliary vibration eccentric block and the main vibration eccentric block is 90 degrees, the probability of the steel wheel separating from the ground can be reduced, the vibration can be avoided, and the uniformity of the compacted soil can be ensured.
Drawings
FIG. 1 is a schematic illustration of the structure of a multi-frequency superimposed vibratory steel wheel of the present invention;
FIG. 2 is a waveform diagram of the wheel body of the embodiment of the invention performing circumferential vibration with an amplitude of 1.0mm, a frequency of 33Hz and an initial phase of 0 DEG under the excitation of the main excitation device;
FIG. 3 is a waveform diagram of the wheel in the embodiment 1 of the present invention, which is excited by the secondary excitation device to perform circumferential vibration with an amplitude of 0.2mm, a frequency of 99Hz and an initial phase of 0 degree;
FIG. 4 is a superimposed waveform diagram of the wheel body of the embodiment 1 of the present invention under simultaneous excitation of the primary excitation device and the secondary excitation device;
FIG. 5 is a waveform diagram of the wheel in example 2 of the present invention performing circumferential vibration with an amplitude of 0.15mm, a frequency of 99Hz, and an initial phase of 0℃under excitation of the secondary excitation device;
FIG. 6 is a superimposed waveform diagram of the wheel body of embodiment 2 of the present invention under simultaneous excitation of the primary excitation device and the secondary excitation device;
FIG. 7 is a waveform diagram of the wheel in accordance with the embodiment 3 of the present invention, which is excited by the secondary excitation device to perform circumferential vibration with an amplitude of 0.4mm, a frequency of 66Hz, and an initial phase of 0 degree;
FIG. 8 is a superimposed waveform diagram of the wheel body of embodiment 3 of the present invention under simultaneous excitation of the primary excitation device and the secondary excitation device;
FIG. 9 is a waveform diagram of the wheel body of the embodiment 4 of the invention performing circumferential vibration with an amplitude of 0.4mm, a frequency of 66Hz and an initial phase of 90 DEG under the excitation of the secondary excitation device;
FIG. 10 is a superimposed waveform diagram of the wheel body of the embodiment 4 of the present invention under simultaneous excitation of the primary excitation device and the secondary excitation device;
FIG. 11 is a waveform diagram of the wheel in example 5 of the present invention performing circumferential vibration with an amplitude of 0.2mm, a frequency of 132Hz, and an initial phase of 0℃under excitation of the secondary excitation device;
fig. 12 is a waveform chart showing superposition of the main excitation device and the auxiliary excitation device for exciting the wheel body simultaneously according to embodiment 5 of the present invention.
In the figure: 1. a wheel body; 11. a damper; 2. a main excitation device; 21. a main excitation eccentric block; 3. a secondary excitation device; 31. and the auxiliary excitation eccentric block.
Description of the embodiments
The present invention will be further described with reference to the drawings (hereinafter, the description will be made with respect to the axial direction of the wheel body 1 as the left-right direction).
As shown in fig. 1, the multi-frequency superposition vibration steel wheel comprises a wheel body 1, a main vibration excitation device 2 and an auxiliary vibration excitation device 3; the wheel body 1 comprises a rim with a cylindrical structure and a plurality of layers of radial plates which are coaxially and fixedly arranged in the rim and are symmetrically arranged relative to the rim left and right along the axial direction, and the radial plates at the outermost layer of the wheel body 1 are used for connecting a steel wheel with a frame or a driving plate of the vibratory roller through a shock absorber 11; the main vibration excitation device 2 is arranged at the geometric center position inside the wheel body 1 through a vibration bearing and a radial plate, the main vibration excitation device 2 comprises a main vibration shaft coaxially arranged with the wheel body 1 and a main vibration eccentric block 21 fixedly arranged on the main vibration shaft and extending out along the radial direction of the main vibration shaft, a main vibration driving mechanism is arranged on the main vibration shaft, and the main vibration shaft can be controlled to drive the main vibration eccentric block 21 to rotate at a high speed to output main vibration force by controlling the action of the main vibration driving mechanism; the auxiliary vibration device 3 is symmetrically arranged left and right relative to the main vibration device 2, namely, the auxiliary vibration device 3 positioned at the left side or the right side of the main vibration device 2 can be arranged into one or more parts, the auxiliary vibration device 3 comprises an auxiliary vibration shaft which is coaxially arranged with the wheel body 1 and an auxiliary vibration eccentric block 31 which is fixedly arranged on the auxiliary vibration shaft and extends out along the radial direction of the auxiliary vibration shaft, an auxiliary vibration driving mechanism is arranged on the auxiliary vibration shaft, the auxiliary vibration driving mechanism is controlled to act, the auxiliary vibration shaft can be controlled to drive the auxiliary vibration eccentric block 31 to rotate at a high speed to output auxiliary vibration force, the fact that the excessive eccentric moment proportion is difficult to realize structurally due to excessive centrifugal force caused by the rotation of the eccentric block or the effect of high frequency caused by the small vibration amplitude is not obvious is avoided, and therefore, the synthetic eccentric distance of all the auxiliary vibration eccentric blocks 31 is limited to 15-40% of the eccentric distance of the main vibration eccentric block 21; in the working state, the auxiliary excitation vibration shafts and the main excitation vibration shafts rotate in the same direction, so that the stability of superposition output is ensured, the rotating speeds of all the auxiliary excitation vibration shafts are the same, and based on the practical application consideration of the vibratory roller, the problem that the model selection of the high-speed bearing is difficult to realize due to overlarge rotating speed multiple difference is solved, so that the stability of superposition output is ensured, and the rotating speed of the auxiliary excitation vibration shafts is limited to be 2 times or 3 times or 4 times (namely, the integral multiple in 2 to 4 times) of the rotating speed of the main excitation vibration shafts.
In order to reduce the arrangement of the mechanism and ensure the synchronism more conveniently, as a further improvement scheme of the invention, the main vibration excitation driving mechanism and the auxiliary vibration excitation driving mechanism share the same vibration excitation driving mechanism, and in order to ensure the balance of vibration excitation, the main vibration excitation driving mechanism and the auxiliary vibration driving mechanism preferably share the same main vibration driving mechanism, and the auxiliary vibration shaft is connected with the main vibration shaft through gear transmission, and the main vibration shaft and the auxiliary vibration shaft can be synchronously driven to rotate in the same direction through the same main vibration driving mechanism which is shared and is positioned at the inner geometric center position of the wheel body 1.
The present invention will be further described below by taking the case where the secondary excitation device 3 is provided in two pieces symmetrically with respect to the primary excitation device 2.
Examples
The synthetic eccentric moment of the two auxiliary excitation eccentric blocks 31 is 20% of the eccentric distance of the main excitation eccentric block 21, the rotating speed of the auxiliary excitation vibration shaft is 3 times of the rotating speed of the main excitation vibration shaft, the initial phase of the main excitation eccentric block 21 is 0, the initial phase difference of the two auxiliary excitation eccentric blocks 31 and the main excitation eccentric block 21 is 0, namely the initial phase of the two auxiliary excitation eccentric blocks 31 is also 0, in the initial state, the centroids of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are positioned in a vertical plane which passes through the central axis of the wheel body 1 and is vertical to the ground, and the gravity directions of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are both directed and vertical to the ground; if the rotation speed of the main excitation vibration shaft of the main excitation device 2 is 1980r/min, the amplitude of the wheel body 1 caused by independent excitation is 1.0mm, under the condition, as shown in fig. 2, the wheel body 1 vibrates circumferentially with the amplitude of 1.0mm, the frequency of 33Hz and the initial phase of 0 under the excitation of the main excitation device 2, and meanwhile, as shown in fig. 3, the wheel body 1 vibrates circumferentially with the amplitude of 0.2mm, the frequency of 99Hz and the initial phase of 0 under the excitation of the auxiliary excitation device 3, the two vibration are overlapped to form special regular double-frequency vibration as shown in fig. 4, the wheel body 1 vibrates with the fundamental frequency of 33Hz and the 3-frequency of the fundamental frequency, and the 33Hz with a certain proportion relation with the inherent frequency of the compacted soil particles can drive the soil particles to move, and the 3-frequency of the fundamental frequency can drive the soil particles to vibrate more rapidly and more times to be in a vibration state, so that the rolling speed and the compacting efficiency are improved on the premise of guaranteeing the uniformity of the soil after compacting.
Examples
The composite eccentric moment of the two auxiliary excitation eccentric blocks 31 is 15% of the eccentric distance of the main excitation eccentric block 21, the rotating speed of the auxiliary excitation vibration shaft is 3 times of the rotating speed of the main excitation vibration shaft, the initial phase of the main excitation eccentric block 21 is 0, the initial phase difference of the two auxiliary excitation eccentric blocks 31 and the main excitation eccentric block 21 is 0, namely the initial phase of the two auxiliary excitation eccentric blocks 31 is also 0, in the initial state, the centroids of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are positioned in a vertical plane which passes through the central axis of the wheel body 1 and is vertical to the ground, and the gravity directions of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are both directed and vertical to the ground; if the rotation speed of the main excitation vibration shaft of the main excitation device 2 is 1980r/min, the amplitude of the wheel body 1 caused during independent excitation is 1.0mm, under the condition, as shown in fig. 2, the wheel body 1 vibrates circumferentially with the amplitude of 1.0mm, the frequency of 33Hz and the initial phase of 0 under the excitation of the main excitation device 2, meanwhile, as shown in fig. 5, the wheel body 1 vibrates circumferentially with the amplitude of 0.15mm, the frequency of 99Hz and the initial phase of 0 under the excitation of the auxiliary excitation device 3, the two vibration are overlapped to form special regular double-frequency vibration as shown in fig. 6, the wheel body 1 vibrates with the fundamental frequency of 33Hz and the fundamental frequency of 3 times, the 33Hz with the natural frequency of the compacted soil particles can drive the soil particles to move, the soil particles can be driven to vibrate for a plurality of times more quickly through the 3 times through the frequency multiplication of the fundamental frequency, so that the rolling speed and the compaction efficiency are improved on the premise of guaranteeing the uniformity of the soil after compaction is realized, in addition, the maximum vibration amplitude can be effectively flattened and reduced through the arrangement, and the jump vibration is avoided.
Examples
The composite eccentric moment of the two auxiliary excitation eccentric blocks 31 is 40% of the eccentric distance of the main excitation eccentric block 21, the rotating speed of the auxiliary excitation vibration shaft is 2 times of the rotating speed of the main excitation vibration shaft, the initial phase of the main excitation eccentric block 21 is 0, the initial phase difference of the two auxiliary excitation eccentric blocks 31 and the main excitation eccentric block 21 is 0, namely the initial phase of the two auxiliary excitation eccentric blocks 31 is also 0, in the initial state, the centroids of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are positioned in a vertical plane which passes through the central axis of the wheel body 1 and is vertical to the ground, and the gravity directions of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are both directed and vertical to the ground; if the rotation speed of the main excitation vibration shaft of the main excitation device 2 is 1980r/min, the amplitude of the wheel body 1 caused during independent excitation is 1.0mm, under the condition, as shown in fig. 2, the wheel body 1 vibrates circumferentially with the amplitude of 1.0mm, the frequency of 33Hz and the initial phase of 0 under the excitation of the main excitation device 2, and meanwhile, as shown in fig. 7, the wheel body 1 vibrates circumferentially with the amplitude of 0.4mm, the frequency of 66Hz and the initial phase of 0 under the excitation of the auxiliary excitation device 3, the two vibration modes are overlapped to form special regular double-frequency vibration as shown in fig. 8, the wheel body 1 vibrates with the fundamental frequency of 33Hz and the fundamental frequency of 2 frequency, the soil particles can be driven to move through the fundamental frequency of 33Hz which has a certain proportion relation with the inherent frequency of the compacted soil particles, the soil particles can be driven to vibrate for more times by the 2 frequency of the fundamental frequency so as to improve the rolling speed and the compaction efficiency on the premise of guaranteeing the uniformity of the soil after compaction.
Examples
The composite eccentric moment of the two auxiliary excitation eccentric blocks 31 is 40% of the eccentric distance of the main excitation eccentric block 21, the rotating speed of the auxiliary excitation vibration shaft is 2 times of the rotating speed of the main excitation vibration shaft, the initial phase of the main excitation eccentric block 21 is 0, the initial phase difference of the two auxiliary excitation eccentric blocks 31 and the main excitation eccentric block 21 is 90 degrees, namely the initial phase of the two auxiliary excitation eccentric blocks 31 is 90 degrees, in the initial state, the mass center of the main excitation eccentric block 21 is positioned in a vertical plane passing through the central axis of the wheel body 1 and vertical to the ground, the gravity direction of the mass center is directed to and vertical to the ground, and the mass center of the auxiliary excitation eccentric block 31 is positioned in a horizontal plane passing through the central axis of the wheel body 1 and parallel to the ground; if the rotation speed of the main excitation vibration shaft of the main excitation device 2 is 1980r/min, the amplitude of the wheel body 1 caused by single excitation is 1.0mm, under the condition, as shown in figure 2, the wheel body 1 vibrates circumferentially with the amplitude of 1.0mm, the frequency of 33Hz and the initial phase of 0 under the excitation of the main excitation device 2, meanwhile, as shown in figure 9, the wheel body 1 vibrates circumferentially with the amplitude of 0.4mm, the frequency of 66Hz and the initial phase of 90 DEG under the excitation of the auxiliary excitation device 3, the two vibration can be overlapped to form special regular double-frequency vibration as shown in figure 10, the wheel body 1 vibrates in a frequency doubling mode of 33Hz and 2 frequency doubling mode of the fundamental frequency, and the fundamental frequency 33Hz with a certain proportion relation with the natural frequency of the compacted soil particles can drive the soil particles to move, the soil particles can be driven to vibrate for multiple times faster through 2 times of fundamental frequency to be in a vibration state, so that rolling speed and compaction efficiency are improved on the premise of guaranteeing uniformity of the compacted soil, in addition, through the arrangement of the phase difference of 90 degrees, after vibration superposition, the upward and downward vibration amplitudes of the wheel body are different, and according to the embodiment, as can be seen from fig. 10, the downward vibration amplitude is about 1.4mm, the upward vibration amplitude is about 0.7mm, and the downward vibration amplitude can be effectively increased relative to the single vibration of only the main vibration excitation device 2, so that the ground acting force is increased, the compaction efficiency is improved, meanwhile, the upward amplitude of the steel wheel is reduced, the probability that the steel wheel is separated from the ground is reduced, the jump vibration is avoided, and the uniformity of the compacted soil is guaranteed.
Examples
The synthetic eccentric moment of the two auxiliary excitation eccentric blocks 31 is 20% of the eccentric distance of the main excitation eccentric block 21, the rotating speed of the auxiliary excitation vibration shaft is 4 times of the rotating speed of the main excitation vibration shaft, the initial phase of the main excitation eccentric block 21 is 0, the initial phase difference of the two auxiliary excitation eccentric blocks 31 and the main excitation eccentric block 21 is 0, namely the initial phase of the two auxiliary excitation eccentric blocks 31 is also 0, in the initial state, the centroids of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are positioned in a vertical plane which passes through the central axis of the wheel body 1 and is vertical to the ground, and the gravity directions of the main excitation eccentric block 21 and the auxiliary excitation eccentric block 31 are both directed and vertical to the ground; if the rotation speed of the main excitation vibration shaft of the main excitation device 2 is 1980r/min, the amplitude of the wheel body 1 caused by independent excitation is 1.0mm, under the condition, as shown in fig. 2, the wheel body 1 vibrates circumferentially with the amplitude of 1.0mm, the frequency of 33Hz and the initial phase of 0 under the excitation of the main excitation device 2, and meanwhile, as shown in fig. 11, the wheel body 1 vibrates circumferentially with the amplitude of 0.2mm, the frequency of 132Hz and the initial phase of 0 under the excitation of the auxiliary excitation device 3, the two vibration are overlapped to form special regular double-frequency vibration as shown in fig. 12, the wheel body 1 vibrates with the fundamental frequency of 33Hz and the fundamental frequency of 4 times, and the 33Hz with a certain proportion relation with the inherent frequency of the compacted soil particles can drive the soil particles to move, and the 4 times of the fundamental frequency can drive the soil particles to vibrate more rapidly and be in a vibration state, so that the rolling speed and the compacting efficiency are improved on the premise of guaranteeing the uniformity of the soil after compacting.
The multi-frequency superposition vibration steel wheel can simultaneously output special regular double-frequency vibration through frequency, amplitude and phase combination, the rolling speed and compaction efficiency can be improved by utilizing high frequency in the vibration steel wheel, the stability of the compaction process and the uniformity of the soil after compaction can be ensured, the special, stable and regular multi-frequency superposition output is adopted, the amplitude of downward vibration can be effectively increased when the initial phase difference of the auxiliary vibration excitation eccentric block 31 and the main vibration eccentric block 21 is 0 degree, the ground acting force of the steel wheel is further increased, the compaction efficiency is improved, the upward amplitude of the steel wheel can be effectively reduced when the initial phase difference of the auxiliary vibration eccentric block 31 and the main vibration eccentric block 21 is 90 degrees, the probability of the steel wheel separating from the ground is further reduced, the jump vibration is avoided, and the uniformity of the soil after compaction is ensured.
Claims (7)
1. The main vibration excitation device (2) is arranged at the geometric center position inside the wheel body (1) through a vibration bearing and a radial plate, the main vibration excitation device (2) comprises a main vibration excitation shaft coaxially arranged with the wheel body (1) and a main vibration excitation eccentric block (21) fixedly arranged on the main vibration excitation shaft and extending out along the radial direction of the main vibration excitation shaft, and a main vibration excitation driving mechanism is arranged on the main vibration excitation shaft;
the auxiliary vibration device (3) is symmetrically arranged left and right relative to the main vibration device (2), the auxiliary vibration device (3) comprises an auxiliary vibration shaft which is coaxially arranged with the wheel body (1) and an auxiliary vibration eccentric block (31) which is fixedly arranged on the auxiliary vibration shaft and extends out along the radial direction of the auxiliary vibration shaft, an auxiliary vibration driving mechanism is arranged on the auxiliary vibration shaft, and the synthetic eccentric distance of all the auxiliary vibration eccentric blocks (31) is 15% -40% of the eccentric distance of the main vibration eccentric block (21);
when the vibration device is in a working state, the auxiliary vibration shafts and the main vibration shafts rotate in the same direction, the rotating speeds of all the auxiliary vibration shafts are the same, and the rotating speed of the auxiliary vibration shafts is 2 times or 3 times or 4 times that of the main vibration shafts.
2. The multi-frequency superimposed vibration steel wheel according to claim 1, characterized in that the initial phase difference of the secondary excitation eccentric mass (31) and the primary excitation eccentric mass (21) is 0 °.
3. The multi-frequency superimposed vibration steel wheel according to claim 1, characterized in that the initial phase difference of the secondary excitation eccentric mass (31) and the primary excitation eccentric mass (21) is 90 °.
4. The multi-frequency superimposed vibration steel wheel according to claim 1, wherein the main excitation driving mechanism and the auxiliary excitation driving mechanism share the same excitation driving mechanism, and the auxiliary excitation vibration shaft is in transmission connection with the main excitation vibration shaft.
5. The multi-frequency superimposed vibratory steel wheel of claim 4, wherein the primary excitation drive mechanism and the secondary excitation drive mechanism share the same primary excitation drive mechanism.
6. The multi-frequency overlay vibratory steel wheel of claim 4, wherein the secondary excitation vibration shaft is geared with the primary excitation vibration shaft.
7. A vibratory roller comprising a multi-frequency stacked vibratory steel wheel as claimed in any one of claims 1 to 6.
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