CN114146902A - Vibration sieve vibration reduction resonance eccentric block and vibration motor - Google Patents
Vibration sieve vibration reduction resonance eccentric block and vibration motor Download PDFInfo
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- CN114146902A CN114146902A CN202111401088.4A CN202111401088A CN114146902A CN 114146902 A CN114146902 A CN 114146902A CN 202111401088 A CN202111401088 A CN 202111401088A CN 114146902 A CN114146902 A CN 114146902A
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- 230000003068 static effect Effects 0.000 claims description 44
- 230000005484 gravity Effects 0.000 claims description 20
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- 230000002829 reductive effect Effects 0.000 abstract description 20
- 230000000694 effects Effects 0.000 abstract description 10
- 230000002411 adverse Effects 0.000 abstract description 6
- 230000000670 limiting effect Effects 0.000 abstract description 6
- 230000002093 peripheral effect Effects 0.000 abstract description 3
- 238000012216 screening Methods 0.000 description 19
- 230000033001 locomotion Effects 0.000 description 13
- 230000006835 compression Effects 0.000 description 9
- 238000007906 compression Methods 0.000 description 9
- 239000000463 material Substances 0.000 description 8
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- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
- B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
- B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
- B07B1/28—Moving screens not otherwise provided for, e.g. swinging, reciprocating, rocking, tilting or wobbling screens
- B07B1/286—Moving screens not otherwise provided for, e.g. swinging, reciprocating, rocking, tilting or wobbling screens with excentric shafts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
- B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
- B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
- B07B1/42—Drive mechanisms, regulating or controlling devices, or balancing devices, specially adapted for screens
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B07—SEPARATING SOLIDS FROM SOLIDS; SORTING
- B07B—SEPARATING SOLIDS FROM SOLIDS BY SIEVING, SCREENING, SIFTING OR BY USING GAS CURRENTS; SEPARATING BY OTHER DRY METHODS APPLICABLE TO BULK MATERIAL, e.g. LOOSE ARTICLES FIT TO BE HANDLED LIKE BULK MATERIAL
- B07B1/00—Sieving, screening, sifting, or sorting solid materials using networks, gratings, grids, or the like
- B07B1/46—Constructional details of screens in general; Cleaning or heating of screens
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
- H02K7/06—Means for converting reciprocating motion into rotary motion or vice versa
- H02K7/061—Means for converting reciprocating motion into rotary motion or vice versa using rotary unbalanced masses
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Abstract
The invention discloses a vibration screen resonance-reducing eccentric block which is characterized in that the eccentric block comprises an eccentric block chassis and a movable balancing weight, wherein an outer track for limiting the movable range of the movable balancing weight is arranged on the eccentric block chassis; the vibrating screen can be set to different proximal positions and distal positions to provide different vibrating forces, so that the resonant amplitude of the vibrating screen is reduced when the vibrating screen is started and stopped to pass through a resonance region, the dynamic load to the ground is reduced, the peripheral components are not impacted due to overlarge amplitude, the adverse effect on the screen body is avoided, the starting and stopping are stable, the starting torque is small, and the starting current is small.
Description
Technical Field
The invention relates to the technical field of vibrating screening, in particular to a vibrating screen resonance-reducing eccentric block and a vibrating motor.
Background
In the prior art, a vibrating screen consists of a motor, a screen body, a vibrator and a supporting component, wherein the vibrator consists of a main shaft or an eccentric shaft, an eccentric block and the like, and a vibrating motor integrating the motor and the vibrator is used as the vibrator. The motor drives the main shaft of the vibrator to rotate, the main shaft is provided with an eccentric block, the main shaft drives the eccentric block to rotate, centrifugal force and inertia force generated by eccentric mass of the eccentric shaft or the eccentric block drive the screening machine to vibrate violently, and the materials are screened according to granularity. The eccentric block generates centrifugal force when rotating at high speed according to the eccentric weight and the eccentric moment of the eccentric block, and can drive a screening machine with the weight of tens of tons to vibrate, and the amplitude of the screening machine is related to the weight of the screening machine and the eccentric static moment of the eccentric block and can be calculated and determined. When the motor and the main shaft work at rated rotating speed, the amplitude of the screening machine is basically stable and unchanged, stable forced vibration is formed, and the passing influence of materials is small. The screening machine body is a rigid structure and has a certain inherent frequency. Shakers typically operate at frequencies far from the natural frequency. If the rated vibration frequency of the vibrating screen works near the natural frequency of the screening machine, the screening machine generates resonance, the amplitude is large, and the influence of the change of materials is large. When the screening machine is started, the rotating speed of the eccentric block is accelerated from zero, the eccentric block passes through the inherent frequency of the screening machine, a resonance effect is generated, the amplitude exceeds more than 5 times of the rated amplitude, a large load to the ground is generated, and the phenomena of overload and resonance of a foundation structure are easily generated; the large-amplitude vibration of the screen machine may impact peripheral fixed components to damage the fixed components and the screen machine body; the resonance is influenced by various aspects, the motion track is irregular, and the torsional pendulum motion in the resonance can have adverse effect on the structure of the screen; the large-amplitude resonance of the screening machine can also influence the stability of the transmission connection of the screening machine and the motor; the shutdown phase also has the same adverse effect as the natural frequency. The motor is started with an eccentric block, so that a large starting torque is needed, a large starting current is generated, and adverse effects are generated on the motor, an electric control system and a power grid.
Therefore, there is a need to reduce the resonant action of the shaker at start-up and shut-down. In the prior art, the resonance amplitude of the screening machine is reduced by using a vibration reduction underframe or a damper, but the vibration reduction underframe is high in cost, and the damper has adverse effect on the screening machine.
201520726899.5 adopts a mode that a spring pulls two swinging eccentric blocks, reduces vibration force and resonance when starting and stopping, but has large centrifugal force at rated speed, and has high requirements on the strength and rigidity of the hinged column of the eccentric block; the requirement on the rigidity of the spring is high, and the volume of the spring is large, so that the negative bias is large; the swinging eccentric block is in the balance of centrifugal force and spring force, once the centrifugal force changes, the position of the swinging eccentric block changes, the motor of the vibrating screen is influenced by the fluctuation of the supplied materials, the rotating speed fluctuates, the position of the swinging eccentric block changes, and the vibrating force also fluctuates; due to the influence of manufacturing errors, the position change between the swinging eccentric blocks is not necessarily synchronous, which further causes the inconsistency of the vibration force of each eccentric block, causes the abnormal motion of the vibrating screen and even causes the damage to the screen machine. 201820033226.5A movable eccentric block is pulled by two springs, because the springs have a certain length, the distance between the mass center of the movable eccentric block and the center of the main shaft can not be reduced to a small value, the movable eccentric block still provides a large centrifugal force when starting, because of the action of the inertia force when starting and stopping, the movable eccentric block can generate unnecessary swing, the centrifugal force of the movable eccentric block is basically pulled by the springs when in rated speed, the requirement on the rigidity of the springs is high, and the change of the rotating speed in working causes the change of the centrifugal force of the movable eccentric block, thereby influencing the stress balance of the movable eccentric block, the fluctuation of the working speed causes the position change of the movable eccentric block, and the provided vibration force also fluctuates.
When the starting of the motor is started, the centrifugal force is increased, the movable eccentric block begins to move outwards, the vibration force is reduced in a limited mode during resonance, and the starting torque is reduced in a limited mode.
There is a need for a more suitable way to reduce the starting torque required during the start-up phase of the shaker, to reduce the resonance effects during start-up and shut-down even more, and to stabilize the shaking forces during operation.
Disclosure of Invention
In order to reduce the starting torque required by the starting stage of the vibrating screen, reduce the resonance action during starting and stopping and stabilize the vibrating force during working, the invention provides a vibrating screen resonance-reducing eccentric block which is also suitable for an eccentric block of a vibrating motor.
The invention adopts the technical scheme that a vibrating screen resonance-reducing eccentric block is provided with a movable balancing weight, the movable balancing weight can move back and forth from the center to the outside along the center of a main shaft, and an outer track which limits the movable range of the movable balancing weight is arranged on a chassis of the eccentric block. When the main shaft is static and rotating at low speed, the movable balancing weight is at a position close to the main shaft center, and when the main shaft rotates at high speed, the movable balancing weight is at a position far from the main shaft center.
The utility model provides a shale shaker subtracts resonance eccentric block, includes eccentric block chassis and the balancing weight that lives, is equipped with the outer track of restriction balancing weight home range on the eccentric block chassis, and the balancing weight that lives is established in outer track, and the balancing weight that lives is connected and is used for pulling or withstands the spring of balancing weight that lives, and outer orbital at least one end is equipped with the nearly heart adjustment mechanism that is used for adjusting nearly heart extreme position or is used for adjusting far heart adjustment mechanism of far heart extreme position.
The proximal adjusting mechanism is a proximal moment adjusting bolt pair.
The telecentric adjusting mechanism is a limit bolt pair or a telecentric moment positioning sleeve.
Preferably, the static moment of the mass center of the eccentric block chassis + the spring is opposite to the static moment of the mass center of the movable balancing weight at the approximate center position, and the static moment are equal in value.
Preferably, the resting or supporting force of the spring is greater than the centrifugal force + the gravity of the movable counterweight at resonance. When the vibrating screen is started and passes through the resonance area, the movable balancing weight does not move outwards; before the vibrating screen stops running through the resonance area, the movable balancing weight returns to the position closest to the axis.
Preferably, the maximum pulling force or supporting force of the limiting position of the spring is less than the centrifugal force minus the gravity of the movable balancing weight at the rated rotating speed. Can adapt to the rotating speed fluctuation during working.
Preferably, the proximal and distal limit positions of the movable weight block are adjustable.
Preferably, the stiffness and compression length of the spring can be adjusted.
Preferably, the loose weight material may be a material heavier than iron. Such as lead, can provide a greater eccentric weight in a smaller volume.
Preferably, the movable weight block may be additionally weighted. So that the provided rated centrifugal force has different values, can match with the vibration weight of different screening machines and make the screening machines generate different amplitudes, and is suitable for different material parameters, throughput and the like.
Preferably, the additional weight on the movable balancing weight can be filled on the front surface of the movable balancing weight, on the back surface of the movable balancing weight, or through holes on the movable balancing weight.
Preferably, the outer track and the eccentric block chassis can form a closed inner cavity, and the inner cavity is filled with grease.
The invention provides a vibrator, wherein the main shaft of the vibrator is provided with the eccentric block.
The invention provides a vibration motor, wherein the two sides of a main shaft of the vibration motor are provided with the eccentric blocks.
The invention also provides a vibrating screen which consists of a motor, a screen body, a vibrator, a supporting component, a main shaft and an eccentric block, and is characterized in that the main shaft of the vibrator of the vibrating screen is provided with the eccentric block comprising the movable balancing weight.
When the motor drives the main shaft and the eccentric block to start, the rotating speed of the main shaft is accelerated from zero to reach the resonant frequency of the screening machine, and at the moment, the movable balancing weight is positioned close to the center of the main shaft, so that the generated centrifugal force is small, and the provided excitation force is small. When the resonance amplitude is 5 times of the rated amplitude, as long as the exciting force of the resonance point is 1/5 of the rated exciting force, the resonance amplitude is equal to the rated amplitude, because the resonance frequency is less than the working rated frequency, and the centrifugal force is far less than the rated centrifugal force. Centrifugal force F ═ mv ^2/r or F ═ m ψ2r, when the resonance frequency is half of the rated frequency, the resonance centrifugal force is only 1/4 of the rated centrifugal force, so when the static moment of the eccentric mass center of mass of the resonance point is half of the rated static moment, F is m0.25 psi20.5r＝0.125mψ2r, i.e., the excitation force at the resonance point, is only 1/8 of the rated excitation force. If the resonant frequency is lower than half the nominal frequency, the resonant excitation force will be lower. When the static moment passing through the resonance area is smaller, the required inertia force is smaller, and the motor can pass through the resonance area more quickly.
An outer track which is used for limiting the moving range of the movable balancing weight is arranged on the eccentric block chassis. The outer track is used for restraining the outer surface of the movable balance weight block and is used as a part of the eccentric chassis for fixing the eccentric weight without occupying a part of the movable balance weight. The track has the function of limiting the extra movement of the movable balancing weight on one hand, such as the outward movement beyond the range, the unnecessary rotation, the swing and the like; the track provides the supporting force to overcome the inertia force at the same time, when starting the acceleration stage and shutting down the deceleration stage, the movable counterweight block has forward or backward inertia force, the side of the track can limit it to exceed the range of motion; when the movable weight block is moved to a position close to the axial center, a rail is required to limit the limit position, and when the movable weight block moves outwards, a rail is also required to limit the limit position. The spring of the invention is mainly responsible for pulling or propping the movable balancing weight not to move outwards in the resonance region, and the centrifugal force of the movable balancing weight at the outermost limit position is mainly balanced by the rail supporting force after the spring force is reduced.
In order to keep the movable balance weight block stably at the position nearest to the main shaft at low speed and not move outwards, a spring is needed to pull or support the movable balance weight block. When the mass point of the movable weight block is closer to the center of the main shaft, the centrifugal force generated by the movable weight block is smaller. The movable balancing weight moves back and forth along the center of the main shaft from the center to the outside, so that the center of mass of the movable balancing weight is very close to the center of the main shaft, and the centrifugal force generated in the resonant frequency interval is very small. Calculating formula F ═ m ψ according to centrifugal force2r, if the distance between the mass center of the movable balancing weight and the center of the main shaft is 1mm, 5mm, 30mm and 80mm, the centrifugal force is 1 time, 5 times, 30 times and 80 times respectively. As long as the machining precision can be achieved and the value is minimized, the required tension or supporting force of the spring is small, the rigidity and the compression amount of the spring can also be small, the size of the spring is small, and the structure is compact. The spring force is the centrifugal force of the resonant frequency of the movable balancing weight plus the gravity of the movable balancing weight. Centrifugal force when the movable balancing weight exceeds the resonance frequency + gravity of the movable balancing weight after the rotating speed of the eccentric block is increased>The movable weight will move outward by the spring force.
The static moment of the mass center of the eccentric block chassis and the spring is opposite to the static moment of the mass center of the movable balancing weight at the position close to the center, and the numerical values are equal. The distance between the center of mass and the center of main axle is the length of force arm, the length of force arm is mass, and the mass is static moment. The static moment value of the nearly-centered position of the movable balancing weight is a small value, the static moment of the chassis of the eccentric block and the spring is equal to the static moment value, the static moment values are opposite, the static moment values are mutually offset, the static moment value synthesized by the whole eccentric block is 0, and the vibration force of the rotation of the eccentric block is 0 when the movable balancing weight is not moved.
The movable balancing weight does not move outwards at low speed, the torque required by starting is reduced, the motor is easy to start, the starting current is reduced, and the influence on the power grid is small. Assuming that the rated rotation speed is 960rpm, the rotation speed of the resonance region is 200-250rpm, the movable balance weight block can be set to move outwards after the spring force is 300rpm, or the movable balance weight block can be set to move outwards after the spring force is 800rpm, and the later enables the starting process of the host to be basically completed, the outward movement of the movable balance weight block is stable and slow, and the peak value of the starting current is obviously reduced. Because the barycenter of the movable balancing weight is very close to the center of the main shaft, the centrifugal force of the movable balancing weight at the position of the off-axis center at the rated rotating speed is also small, and the required spring force is also small, otherwise, the centrifugal force is too large, the required spring force is very large, the spring is thick, and the movable balancing weight is difficult to arrange structurally.
When the rotating speed of the main shaft exceeds the resonance frequency and the centrifugal force of the movable balancing weight exceeds the pulling force or the supporting force of the spring, the spring is stretched or compressed to be shortened, so that the movable balancing weight moves outwards from the position close to the axis, the rotating speed is higher and higher, and a larger centrifugal force is generated at the same time, so that the spring is longer and shorter and longer, the centrifugal limit position of the movable balancing weight is reached, a rated centrifugal force is generated, and the movable balancing weight works at a rated rotating speed and a rated centrifugal force.
The tension or pressure of the spring at the limit position should be smaller than the rated centrifugal force by a proper value, so that the movable balancing weight can not move centripetally along with the small reduction of the centrifugal force when the rotating speed of the main shaft fluctuates in a certain range from the rated rotating speed. That is, the rotation speed of the main shaft can fluctuate within a certain range, but the movable weight block is always in the limit position. The inconsistent vibration force of each eccentric block can not be generated due to the influence of manufacturing errors, and the abnormal motion of the vibrating screen can not be caused. This suitable value needs to be adjusted according to the fluctuation range of the rated operating rotational speed of different devices. The rotating speed of the movable balancing weight when reaching the telecentric limit position is lower than the lower limit of the fluctuation range of the working rotating speed of the equipment.
When the rotating speed of the main shaft is reduced by a certain range, the main shaft is actually in a power-off shutdown state, the rotating speed of the main shaft is reduced all the time, and a centrifugal force formula F is m psi2F in r is rapidly reduced along with the reduction of the angular velocity psi, and when the centrifugal force of the movable balancing weight is smaller than the pulling force or the supporting force of the spring, the movable balancing weight starts to centripetally move, and the static moment is reduced. Before the rotation speed of the main shaft is reduced to the resonant frequency range, the movable balance weight block should return to the limit position nearest to the shaft center, so that a smaller resonant amplitude is generated at the resonant frequency. Meanwhile, because the mass center moves centripetally, the inertia force is reduced in acceleration, so that the main shaft can stop rotating faster and pass through a resonance area faster.
If the screen has multiple operating frequencies, it should be considered at the lowest operating frequency. The sieve can still keep the stability of the movable balancing weight when the sieve is near the lowest working frequency. The length of the spring can also be adjusted to make the spring force appropriate.
The invention also provides a vibration screen resonance-reducing eccentric block adjusting method, and the proximal and distal limit positions of the movable balancing weight can be adjusted. The eccentric block is adjusted at the near-center position, so that the static moment of the eccentric block can be adjusted during starting, machining errors are eliminated, and the matched eccentric blocks have the same initial static moment. The static moment of the movable balancing weight can be adjusted to be a proper value, and the matched eccentric blocks move outwards at the same and proper rotating speed at the same time, so that the difference of the initial rotating speeds of the moving blocks is avoided. The telecentric position is adjusted, different rated working static moments can be set to generate different vibration forces, or different vibration amplitudes are generated aiming at different vibration hosts.
Preferably, the stiffness and compression length of the spring can be adjusted. The initial tension or pressure of the spring is adjusted to ensure that the initial rotating speeds of the movable balancing weight moving outwards are different, so that the requirement of different host parameters is met.
The outer track and the eccentric block chassis can form a closed inner cavity, and the inner cavity is filled with grease. The movable balancing weight can move in the cavity, the speed is gentle, the friction is less, and the impact is light.
The invention provides a vibrator, wherein the main shaft of the vibrator is provided with the eccentric block. The vibrators are various, such as eccentric block vibrators, eccentric blocks are arranged on two sides of the main shaft, the bearing seat is arranged on a side plate of the vibrating screen, the two side plates are respectively provided with a vibrator, and the vibrators are connected by universal joints or flexible rod pieces; the box type vibrator has box body mounted on the main beam of the vibrating screen, eccentric blocks mounted on two sides of the main shaft, and double main shafts connected via gears.
The invention provides a vibration motor, wherein the two sides of a main shaft of the vibration motor are provided with the eccentric blocks. The eccentric blocks on the two sides of the vibration motor in the prior art are replaced by the eccentric blocks. The eccentric block in the prior art can change the included angle of the two eccentric blocks to set the vibration force of the vibration motor. The eccentric blocks can be arranged on two sides of the main shaft of the vibration motor, and the vibration force of the vibration motor can be set by replacing the balance weight or the material of the movable balancing weight or setting the working position of the movable balancing weight.
The invention also provides a vibrating screen which consists of a motor, a screen body, a vibrator, a supporting component, a main shaft and an eccentric block, and is characterized in that the eccentric block is arranged on the main shaft of the vibrator of the vibrating screen.
The invention discloses a vibration screen resonance-reducing eccentric block. The eccentric block is also suitable for the vibrating motor and the eccentric block of the feeding machine. The eccentric block is provided with a movable balancing weight which can move back and forth along the center of the main shaft from the center to the outside, and the chassis of the eccentric block is provided with an outer track which limits the moving range of the movable balancing weight; when the main shaft is static and rotates at a low speed, the movable balancing weight is positioned at a position which is extremely close to the main shaft center, and when the main shaft rotates at a high speed, the movable balancing weight is positioned at a position which is far away from the main shaft center; different proximal positions and distal positions can be set, different vibration forces are provided, the vibration amplitude of the vibrating screen is reduced when the vibrating screen is started and stopped to pass through a resonance region, the earth dynamic load is reduced, adverse effects on the screen body due to the fact that the peripheral component is impacted by too large amplitude are avoided, the starting and stopping are stable, the starting torque is small, and the starting current is small.
Drawings
FIG. 1 is a static schematic view of a first embodiment of a resonant vibration-reducing eccentric mass of the present invention.
FIG. 2 is a schematic rotational speed rating for a first embodiment of a resonant vibration-reducing eccentric mass of the present invention.
FIG. 3 is a static schematic view of a second embodiment of a resonant vibration-reducing eccentric mass of the present invention.
FIG. 4 is a schematic rotational speed rating for a second embodiment of a resonant vibration-reducing eccentric mass of the present invention.
FIG. 5 is a schematic view of the closed cavity of the resonance-damping eccentric mass of the vibrating screen of the present invention
FIG. 6 is a schematic view of a vibration motor for reducing resonance of an eccentric mass of a vibrating screen according to the present invention
In the figure, 1, an eccentric block chassis A; 2. a straight guide rail A; 3. pulling the spring; 4. a movable counterweight A; 5. a limiting bolt pair; 6. an eccentric block chassis B; 7. a near-center-moment adjusting bolt pair; 8. a movable counterweight B; 9. pressing a spring; 10. a straight guide rail B; 11. a telecentric moment positioning sleeve; 12. an eccentric block chassis C; 13. the eccentric block is coupled with a shaft closing plate. 14. A vibration motor; 15. an eccentric mass.
Detailed Description
In order to better understand the technical solution, the technical solution will be described in detail with reference to the drawings and the specific embodiments.
FIG. 1 is a static schematic view of a first embodiment of a resonant vibration-reducing eccentric mass of the present invention. In fig. 1, the eccentric mass chassis a1 adopts the pull spring 3 to pull the movable counterweight block a4, the eccentric mass chassis a1 is provided with a straight guide rail a2, and the movable counterweight block a4 can move linearly in the guide rail range of the straight guide rail a 2. The eccentric block chassis A1 is also an eccentric structure and can provide a fixed eccentric static moment to match the insufficient centrifugal force of the movable counterweight block A4; if the working condition that the centrifugal force of the movable balancing weight A4 is proper is adopted, the eccentric block chassis A1 can adopt a non-eccentric structure with the center of gravity at the axis, and even a slightly negative eccentric structure. The eccentric block chassis A1 has a support for fixing the pull spring 3 on one side to fix one end of the pull spring 3, and the other end of the pull spring 3 is fixed on the movable counterweight A4 to provide a proper pulling force for pulling the movable counterweight A4, so that the movable counterweight A4 moves in a specified manner. The eccentric block chassis A1 is coupled with the main shaft by way of a back shaft sleeve. The movable weight a4 has a center of gravity a small suitable distance from the axis. When the eccentric block is static, the pull spring 3 pulls the movable balancing weight A4 to be at the position closest to the axle center, and at the moment, the gravity of the movable balancing weight A4 is mainly overcome and does not fall down due to the gravity; when the movable balancing weight A4 rotates at a low speed in front of the resonance area, a centrifugal force is generated by the dynamics of pressing, at this time, the pulling force of the pulling spring 3 should pull the movable balancing weight A4, and when the resonance area exists, the movable balancing weight A4 does not move outwards, and the pulling force of the pulling spring 3 should be greater than the gravity of the movable balancing weight A4 plus the centrifugal force of the movable balancing weight A4.
One end of the straight guide rail A2 is provided with a limit bolt pair 5 for adjusting the telecentric position of the movable balancing weight, so that the mass center moment of the movable balancing weight can be adjusted according to the requirement. The far end of the straight track A2 is processed with a threaded hole, and the matched limit bolt pair 5 is positioned at a proper position and is firmly positioned by a nut. When the movable balancing weight moves outwards, the movable balancing weight contacts the limiting bolt pair 5 firstly. The length of the limit bolt pair 5 extending into the straight track A2 is different, and the telecentric position of the movable balancing weight A4 is limited at different positions, so that the purpose of different vibration forces of the equipment is achieved. The telecentric position is adjusted, different rated working static moments can be set to generate different vibration forces, or different vibration amplitudes are generated aiming at different vibration hosts.
If the eccentric block chassis A1 is of a structure with the same center of gravity, the generated centrifugal force is the minimum centrifugal force of the movable balancing weight A4; if the eccentric mass centrifugal moment of the eccentric mass chassis A1 is opposite to the minimum centrifugal moment of the movable balance weight A4 mass center and the static moments are equal, then in the resonance region, the vibration force provided by the eccentric mass is zero, and at the moment, no resonance phenomenon should be generated.
FIG. 2 is a schematic rotational speed rating for a first embodiment of a resonant vibration-reducing eccentric mass of the present invention. In the figure, the movable balancing weight A4 overcomes the pulling force of the pulling spring 3 and moves to a centrifugal limit position under the action of centrifugal force to generate rated centrifugal force and drive the screening machine to generate rated amplitude.
The specific process is that after the rotating speed of the spindle exceeds the resonance region, the centrifugal force of the movable balancing weight A4 and the gravity of the movable balancing weight A4 are greater than the pulling force of the pulling spring 3, at this time, the movable balancing weight A4 starts to move outwards along the straight guide rail A2, the outward movement also causes the increase of the pulling force of the pulling spring 3, therefore, the increase of the centrifugal force generated by the movable balancing weight A4 is greater than the boosting force of the pulling spring 3, the pulling spring 3 can not be continuously extended until the movable balancing weight A4 reaches the centrifugal limit position of the straight guide rail A2, and the movable balancing weight A4 is restrained by the limit track of the straight guide rail A2 and does not move outwards any more. If the centrifugal force of the movable balance weight A4 is still increased, the support force provided by the straight guide rail A2 restrains the movable balance weight A4 until the rated rotation speed of the spindle, and the centrifugal force of the movable balance weight A4 is not increased. The pulling force of the pull spring 3 when the movable counterweight block A4 reaches the limit length should be less than the centrifugal force of the movable counterweight block A4 at the limit position to reduce the gravity of the movable counterweight block A4. This difference should be able to accommodate the rotational speed fluctuations of the spindle during operation without centripetal movement of the loose weight block a4 to provide a steady centrifugal force. When the main shaft rotates at a stop, but the rotating speed is reduced to a certain value, the centrifugal force of the movable balancing weight A4 is smaller than the pulling force of the pulling spring 3, the movable balancing weight A4 is pulled to the axis by the pulling force of the pulling spring 3, before the rotating speed of the main shaft is reduced to a resonance area, the movable balancing weight A4 is pulled to the limit position closest to the axis, the centrifugal force generated by the movable balancing weight A4 is minimum, and the excitation effect generated by the eccentric mass in the resonance area is minimum.
Figure 3 is a static schematic view of a second embodiment of a vibrating screen loose eccentric mass of the present invention. In the figure, an eccentric block chassis B6 adopts a compression spring 9 to prop against a movable balancing weight B8, a straight guide rail B10 is arranged on an eccentric block chassis B6, and the movable balancing weight B8 can move linearly in the guide rail range of a straight guide rail B10. The eccentric block chassis B6 is also an eccentric structure and can provide a fixed eccentric static moment to match the insufficient telecentric static moment of the movable balancing weight B8;
one end of the pressure spring 9 is supported on the centrifugal limit guide rail of the eccentric block chassis B6, and the other end of the pressure spring 9 is fixed on the movable balancing weight B8 to provide a proper supporting force for supporting the movable balancing weight B8, so that the movable balancing weight B8 generates a specified movement. The eccentric mass pan B6 is also coupled to the main shaft in the manner of a back sleeve. The center of gravity of the movable weight block B8 is a small proper distance from the axis. When the eccentric block is static, the pressure spring 9 props against the movable balancing weight B7 to be positioned at the position closest to the axis, and at the moment, the gravity of the movable balancing weight B8 is mainly overcome and does not fall down due to the gravity; when the movable balancing weight B8 rotates at a low speed in front of the resonance area, a centrifugal force is generated by the dynamics, at this time, the supporting force of the pressure spring 9 should prop against the movable balancing weight B8, when the resonance area is reached, the movable balancing weight B8 does not move outwards, the supporting force of the pressure spring 9 should be greater than the gravity of the movable balancing weight B8 + the centrifugal force of the movable balancing weight B8, when the rotating speed of the main shaft exceeds the resonance area, the centrifugal force of the movable balancing weight B8 + the gravity of the movable balancing weight B8 are greater than the supporting force of the pressure spring 9, at this time, the movable balancing weight B8 starts to move outwards along the straight guide rail B10, the supporting force of the pressure spring 9 is increased due to the outward movement, therefore, the increase of the centrifugal force generated by the movable balancing weight B8 should be greater than the boosting force of the pressure spring 9, the pressure spring 9 can not be compressed continuously until the movable balancing weight B8 reaches the centrifugal limit position of the straight guide rail B10, the movable balancing weight B8 is restrained by the limit rail B10, no longer moving outwardly. If the centrifugal force of the movable balancing weight B8 is still increased, the supporting force provided by the straight guide rail B10 restrains the movable balancing weight B8 until the rated rotation speed of the spindle, and the centrifugal force of the movable balancing weight B8 is not increased any more. The supporting force of the compression spring 9 when the movable balance weight B8 reaches the limit length should be smaller than the centrifugal force of the movable balance weight B8 at the limit position to reduce the gravity of the movable balance weight B8. This difference should be able to accommodate the rotational speed fluctuations of the spindle during operation without centripetal movement of the clump weight B8, so as to provide a steady centrifugal force. When the main shaft rotates at a low speed, the centrifugal force of the movable balancing weight B8 is less than the supporting force of the pressure spring 9, the movable balancing weight B8 is pushed to the axis by the supporting force of the pressure spring 9, before the main shaft rotates to the resonance area, the movable balancing weight B8 is pushed to the limit position closest to the axis, the centrifugal force generated by the movable balancing weight B8 is minimum, and the excitation effect generated by the eccentric block in the resonance area is minimum.
One end of the straight guide rail B10 is provided with a near-center-moment adjusting bolt pair 7, a near-center end of the straight guide rail B10 is provided with a threaded hole, and a bolt of the near-center-moment adjusting bolt pair 7 is arranged in the threaded hole, so that the bolt extends into the straight rail B10 with proper size and is firmly positioned by using a nut. The eccentric block is adjusted at the near-center position, so that the static moment of the eccentric block can be adjusted during starting, machining errors are eliminated, and the matched eccentric blocks have the same initial static moment. The static moment of the movable balancing weight can be adjusted to be a proper value, and the matched eccentric blocks move outwards at the same and proper rotating speed at the same time, so that the difference of the initial rotating speeds of the moving blocks is avoided.
The other end of the straight guide rail B10 is provided with a telecentric moment positioning sleeve 11. The telecentric moment positioning sleeve 11 is sleeved outside the compression spring 9, and different heights of the telecentric moment positioning sleeve can position different telecentric positions of the movable balancing weight B8, so that the eccentric block provides different vibration forces during rated operation.
FIG. 4 is a schematic rotational speed rating for a second embodiment of a resonant vibration-reducing eccentric mass of the present invention. In the figure, the movable balancing weight B7 overcomes the supporting force of the compression spring 8 and moves to a centrifugal limit position under the action of centrifugal force to generate rated centrifugal force and drive the screen machine to generate rated amplitude.
The telecentric moment positioning sleeve 11 is sleeved outside the compression spring 9, and positions the telecentric position of the movable balancing weight B8 according to the height of the telecentric moment positioning sleeve, so that the eccentric block provides different vibration forces during rated work.
FIG. 5 is a schematic view of the closed cavity of the resonance-damping eccentric mass of the vibrating screen of the present invention. The cavity in the eccentric block chassis C12 can be filled with the movable balance weight B8 and the compression spring 9, and oil ester is injected, and then the cavity is closed by the eccentric block coupling closing plate 13. The movable balancing weight B8 moves in the cavity, and oil ester is used as a buffering agent and a lubricating agent, so that the oil balancing weight B8 moves stably, the impact is light, the friction with the guide rail is small, and the abrasion between the guide rail and the movable balancing weight is small. The eccentric block coupling closing plate 13 is provided with a coupling sleeve which can be connected with a shaft head of a transmission mechanism to transmit power.
FIG. 6 is a schematic view of a vibration motor for reducing resonance of an eccentric mass of a vibrating screen according to the present invention. In the figure, 14 is a vibration motor main body, and the eccentric blocks 15 of the invention are installed at two ends of a motor main shaft. The vibrating motor can be used on a vibrating screen, a feeder, an ore feeder and a vibrating bin device. Different vibratory forces can be set by changing different telecentric moment positioning sleeves, and different vibratory forces can also be set by changing different movable balancing weights.
While preferred embodiments of the present invention have been described, additional variations and modifications in those embodiments may occur to those skilled in the art once they learn of the basic inventive concepts. Therefore, it is intended that the appended claims be interpreted as including preferred embodiments and all such alterations and modifications as fall within the scope of the invention.
It will be apparent to those skilled in the art that various changes and modifications may be made in the present invention without departing from the spirit and scope of the invention. Thus, if such modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to include such modifications and variations.
Claims (10)
1. The utility model provides a shale shaker subtracts resonance eccentric block, characterized by, eccentric block includes eccentric block chassis and the balancing weight that lives, is equipped with the outer track of restriction balancing weight home range on the eccentric block chassis, and the balancing weight that lives is established in outer track, and the balancing weight that lives is connected and is used for pulling or withstands the spring of balancing weight that lives, and outer orbital at least one end is equipped with the nearly heart adjustment mechanism that is used for adjusting nearly heart extreme position or is used for adjusting far heart adjustment mechanism of far heart extreme position.
2. The vibrating screen resonance-damping eccentric mass of claim 1, wherein said proximal adjustment mechanism is a proximal moment adjustment bolt pair.
3. The vibration screen resonance-reducing eccentric block as set forth in claim 1, wherein said telecentric adjustment mechanism is a stop bolt pair or a telecentric moment positioning sleeve.
4. The vibration screen resonance-reducing eccentric block as set forth in claim 1, wherein the sum of the static moment of the center of mass of the eccentric block chassis and the spring is opposite to the static moment of the center of mass of the movable counter weight in the direction of the centroid, and has the same value.
5. The vibrating screen resonance-reducing eccentric block as set forth in claim 1, wherein the static tension or supporting force of the spring is greater than the sum of the centrifugal force and the gravity of the movable weight block at resonance, and the maximum tension or supporting force at the extreme position of the spring is less than the centrifugal force minus the gravity of the movable weight block at rated rotation speed by a certain value.
6. The vibration screen resonance-reducing eccentric block as set forth in claim 1, wherein the outer rail and the eccentric block bottom plate form a closed inner cavity, and the inner cavity is filled with grease.
7. A vibrator, characterized in that the eccentric mass according to any of claims 1-7 is mounted on the main shaft of the vibrator.
8. A vibration motor, characterized in that the eccentric mass of any one of claims 1 to 7 is installed on both sides of a main shaft of the vibration motor.
9. A vibrating screen, characterized in that the eccentric mass according to any one of claims 1-7 is mounted on the main shaft of the vibrator of the vibrating screen.
10. A vibration sieve vibration reduction resonance eccentric block adjusting method is characterized in that the proximal and distal limit positions of a movable balancing weight can be adjusted; the eccentric block is adjusted at the approximate center position, the static moment of the eccentric block is adjusted when the eccentric block is started, so that the matched eccentric blocks have the same initial static moment, the static moment of the movable balancing weight can also be adjusted to be a proper value, the matched eccentric blocks move outwards at the same and proper rotating speed, and the difference of the moving initial rotating speeds cannot be caused; the telecentric position is adjusted, different rated working static moments can be set to generate different vibration forces, or different vibration amplitudes are generated aiming at different vibration hosts.
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| CN202111401088.4A CN114146902A (en) | 2021-11-24 | 2021-11-24 | Vibration sieve vibration reduction resonance eccentric block and vibration motor |
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Cited By (1)
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| CN114700245A (en) * | 2022-04-18 | 2022-07-05 | 东北大学秦皇岛分校 | Vibration device with excitation force self-adjusting function and parameter determination method thereof |
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Application publication date: 20220308 |