CN105057190A - Inertial excitation device capable of eliminating resonance - Google Patents
Inertial excitation device capable of eliminating resonance Download PDFInfo
- Publication number
- CN105057190A CN105057190A CN201510425321.0A CN201510425321A CN105057190A CN 105057190 A CN105057190 A CN 105057190A CN 201510425321 A CN201510425321 A CN 201510425321A CN 105057190 A CN105057190 A CN 105057190A
- Authority
- CN
- China
- Prior art keywords
- main shaft
- large main
- column
- band
- passage
- 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.)
- Granted
Links
Landscapes
- Vibration Prevention Devices (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Abstract
The invention discloses an inertial excitation device capable of eliminating resonance. The inertial excitation device comprises a large main shaft, an eccentric weight block, a small main shaft, ring devices and a supporting device, wherein a center hole is formed in one end of the large main shaft; the eccentric weight block is fixedly arranged at the other end of the large main shaft; a shaft shoulder at one end of the small main shaft is in sliding fit with the center hole of the large main shaft, and the other end of the small main shaft is vertically and fixedly connected with a rotary shaft; the shaft shoulder of the small main shaft is limited by the bottom face of the center hole and an end cap arranged at the opening of the center hole in the sliding direction; a buffering spring is arranged between the end face of the shaft shoulder and the end cap; the ring devices are arranged at the upper end and the lower end of the large main shaft; the supporting device supports the ring device. A brand new structural design is adopted for the inertial excitation device, resonance of an inertial vibration machine is fundamentally eliminated, stable operation of the device is guaranteed, and the probability that the device is damaged is greatly lowered. Operation of the inertial excitation device is guaranteed through compression performance of the spring, and reliability in the use process is guaranteed. Besides, the inertial excitation device is compact in structure, simple in machining technology and low in production cost.
Description
Technical field
The invention belongs to vibrating machine inertial excitation technical field, particularly a kind of can the inertial excitation device of Damping resounding.
Background technology
Inertia-type vibrating machine is usually used in the screening of material, dehydration, conveying, feed, fragmentation, powder, knockout, shaping, and vibrate and press in the various work such as road, it is most widely used in vibrating machine.Current most of inertia-type vibrating machine all works under the state of super resonance far away; in startup and stopping process, excited frequency is equal with intrinsic frequency sometime and cause larger transient state to resonate to beat; larger instrantaneous amplitude and longer walk time can be produced; equipment not only can be made to destroy; jeopardize factory building safety, also can increase energy consumption.
In order to suppress the transient state of vibrating machine to resonate, the main method adopted at present is that spring automatic aligning is to alleviate the impact of resonance.But this kind of method does not eliminate the impact of resonance, just reduces the peak swing of resonance, does not solve resonance problem thoroughly.
Summary of the invention
The object of the present invention is to provide a kind of can improve vibratory equipment operation stability and service life can the inertial excitation device of Damping resounding.
The technical solution realizing the object of the invention is:
Can the inertial excitation device of Damping resounding, comprising:
One end has the large main shaft of centre bore,
Be fixedly installed on the weighting block of the large main shaft other end,
The shaft shoulder and the large spindle hole of one end are slidably matched, and the other end is configured in the primary spindle be connected with rotational axis vertical,
The shaft shoulder of primary spindle is by the bottom surface of centre bore and be arranged on the end cap of centre bore opening part at glide direction upper limit, and is provided with buffer spring between the end face of the shaft shoulder and end cap,
Be arranged on the circle ring device at the upper and lower two ends of large main shaft;
Support the bracing or strutting arrangement of circle ring device,
Wherein, large main shaft circumferentially has the first cambered surface cannelure, and the first cambered surface cannelure has away from the side of weighting block the second cambered surface cannelure that diameter is greater than the first cambered surface cannelure;
Circle ring device is connected by the annulus cover plate away from large spindle end by the annulus of two coaxial Different Diameter, two annulus surround circular passage, by being respectively arranged with by the spacing great circle band of column of circular passage in the vertical direction away from large spindle end to large major axes orientation in circular passage, pretightning force is had in original state and the first Compress Spring be connected with the great circle band of column between the great circle band of column and slip Circular Plate, annular boss on the circular passage inwall spacing to slip Circular Plate in the vertical direction, two ends are respectively by slip Circular Plate and the roundlet band of column spacing and the second Compress Spring be connected with the roundlet band of column and the roundlet band of column, the roundlet band of column has two states in the first cambered surface cannelure and the second cambered surface cannelure.
The present invention compared with prior art, its remarkable advantage:
(1) present invention employs brand-new structural design, fundamentally eliminate the resonance of inertia-type vibrating machine, ensure that the smooth operation of equipment, the probability making equipment occur to destroy reduces greatly.
(2) the present invention does not adopt high-precision electronic equipment, but the compression performance that make use of spring cleverly carrys out work, ensure that the reliability in use procedure.
(3) compact conformation of the present invention, processing technology is simple, and production cost is low.
Below in conjunction with accompanying drawing, the present invention is described in further detail.
Accompanying drawing explanation
Fig. 1 is that the present invention can the perspective view of inertial excitation device of Damping resounding.
Fig. 2 is that the present invention can the structural representation of inertial excitation device original state of Damping resounding.
Fig. 3 is that the present invention the inertial excitation device of Damping resounding can reach the structural representation of duty at motor speed.
Fig. 4 is that the present invention can the structural representation of the large main shaft of inertial excitation device of Damping resounding.
Fig. 5 is that the present invention can the structural representation of inertial excitation device circle ring device of Damping resounding.
Fig. 6 is that the present invention can the perspective view of inertial excitation device circle ring device of Damping resounding.
Fig. 7 is that the present invention can the perspective view of inertial excitation device slip Circular Plate of Damping resounding.
Detailed description of the invention
Composition graphs 1 ~ Fig. 7:
The present invention is a kind of can the inertial excitation device of Damping resounding, comprising:
One end has the large main shaft 1 of centre bore 17,
Be fixedly installed on the weighting block 2 of large main shaft 1 other end,
The shaft shoulder and large main shaft 1 centre bore of one end are slidably matched, and the other end is configured in the primary spindle 16 be connected with rotational axis vertical,
The shaft shoulder of primary spindle 16 is by the bottom surface of centre bore 17 and be arranged on the end cap 15 of centre bore 17 opening part at glide direction upper limit, and is provided with buffer spring 14 between the end face of the shaft shoulder and end cap 15,
Be arranged on the circle ring device 4 at large main shaft about 1 two ends;
Support the bracing or strutting arrangement 7 of circle ring device 4,
Wherein, large main shaft 1 circumferentially has the first cambered surface cannelure 18, first cambered surface cannelure 18 and has away from the side of weighting block 2 the second cambered surface cannelure 19 that diameter is greater than the first cambered surface cannelure 18;
Circle ring device 4 is connected by the annulus cover plate 5 away from large main shaft 1 end by the annulus of two coaxial Different Diameter, two annulus surround circular passage 6, by being respectively arranged with by the spacing great circle band of column 8 of circular passage 6 in the vertical direction away from large spindle end to large major axes orientation in circular passage 6, pretightning force is had in original state and the first Compress Spring 9 be connected with the great circle band of column 8 between the great circle band of column 8 and slip Circular Plate 10, annular boss 11 on the circular passage inwall spacing to slip Circular Plate 10 in the vertical direction, two ends are respectively by slip Circular Plate 10 and the roundlet band of column 13 spacing and the second Compress Spring 12 be connected with the roundlet band of column 13 and the roundlet band of column 13, the roundlet band of column 13 has two states in the first cambered surface cannelure 18 and the second cambered surface cannelure 19.
Weighting block 2 is by the shaft shoulder on large main shaft 1 and axially spacing at large main shaft 1 of circlip 3 that snap in circlip groove, the correspondence position of the outside wall surface of large main shaft 1 and the internal face of weighting block 2 has keyway, is provided with the flat key of weighting block 2 at the radial upper limit of large main shaft 1 in keyway.
Flat key adopt A type flat key.
Two annulus of circle ring device 4 are connected away from the annulus cover plate 5 of large main shaft 1 end with through the connecting bolt that annulus cover plate 5 stretches into two two annulus end faces respectively by it.
First cambered surface cannelure 18 equal diameters on the roundlet band of column 13 diameter and large main shaft 1, circular passage 6 in the vertical direction divides two sections, the channel width of long-range main shaft 1 end is greater than the passage of nearly large main shaft 1 end, the roundlet band of column 13 diameter matches with the width of the passage of nearly large main shaft 1 end in circular passage 6, and the diameter of the great circle band of column 8 matches with the width of the passage of circular passage 6 long-range main shaft 1 end.
The operation principle of this device and the course of work:
When vibratory equipment starts, rotating shaft drives weighting block 2 to rotate by primary spindle 16 and large main shaft 1, when just starting, the centrifugal intertia force of weighting block 2 and the roundlet band of column 13 are to the axial action dynamic balance of large main shaft 1, when therefore just starting, although the primary spindle 16 be connected with equipment is rotating, be not subject to the effect of centrifugal force, so equipment does not vibrate.Masterpiece is now used on the circle ring device 4 that contacts with the roundlet band of column 13, only has this circle ring device 4 in vibration.When rotating shaft running speed improves, after having crossed resonant frequency.By certain state modulator, along with the increase of the centrifugal force of weighting block 2, the roundlet band of column 13 is by upwards jack-up, and large main shaft 1 just can extend in radial direction, give primary spindle 16 by the centrifugal force of weighting block 2 by buffer spring 14 transmission, thus drive vibration equipment.The frequency that now inertia vibration generator is applied to equipment have passed through resonant frequency, so just eliminates resonance.First Compress Spring 9 has certain pretightning force, and be pressed in slip Circular Plate 10, slip Circular Plate 10 contacts with annular boss 11, and making the first Compress Spring 9 apply pretightning force can realize.When the roundlet band of column 13 is by jack-up, power is passed to the first Compress Spring 9 by slip Circular Plate 10 by the second Compress Spring 12, the size of power equals the pretightning force of the first Compress Spring 9, now slip Circular Plate 10 just can be promoted, first Compress Spring 9 and the second Compress Spring 12 are connected, and spring global stiffness just can reduce.This object is to allow the active force between the roundlet band of column 13 and large main shaft 1 reduce, thus subtracts the frictional force between them.The second cambered surface cannelure 19 on large main shaft 1 is the contacts area in order to increase the roundlet band of column 13 and large main shaft 1, thus greatly reduces the wearing and tearing of equipment.After this, equipment descends smooth working in working order, well protects equipment.
When shutting down, because rotating speed reduces, the centrifugal force of weighting block 2 reduces, and under the effect of buffer spring 14, large main shaft 1 is towards rotating shaft center's motion, and weighting block 2 just can reduce to the distance of equipment center.Because (Fe is centrifugal force to F=m (w^2) R; m is the quality of weighting block 2; w is angular speed; R is the distance of weighting block 2 to center), (Fk is the elastic force of buffer spring to large main shaft to Fk=kx, and k is the rigidity of buffer spring; x is the variable quantity of the length of buffer spring); along with the carrying out of stopping process, R reduces, and w reduces.Therefore, Fe reduces faster than Fk, and weighting block 2 there has been the acceleration towards central motion.Therefore, more and more faster towards central motion of weighting block 2, makes weighting block 2 have certain speed to central motion.By certain optimum configurations, under the effect of inertia, can before resonance point arrives, the roundlet band of column 13 is made to get back in the first cambered surface cannelure 18 again, like this, when resonating, and for example noted earlier, the centrifugal force of weighting block 2 is acted on circle ring device 4 by the roundlet band of column 13, avoids the generation of resonance.By the first Compress Spring 9 and the second Compress Spring 12 and buffer spring 14, the matched design of the parameter of the roundlet band of column 13, can make vibrating machine start and the resonance in the stage of shutdown is eliminated, improve the stability of machinery.
Claims (6)
1. can the inertial excitation device of Damping resounding, it is characterized in that: comprising:
One end has the large main shaft (1) of centre bore (17),
Be fixedly installed on the weighting block (2) of large main shaft (1) other end,
The shaft shoulder and large main shaft (1) centre bore of one end are slidably matched, and the other end is configured in the primary spindle (16) be connected with rotational axis vertical,
The shaft shoulder of primary spindle (16) is by the bottom surface of centre bore (17) and be arranged on the end cap (15) of centre bore (17) opening part at glide direction upper limit, and be provided with buffer spring (14) between the end face of the shaft shoulder and end cap (15)
Be arranged on the circle ring device (4) at the upper and lower two ends of large main shaft (1);
Support the bracing or strutting arrangement (7) of circle ring device (4),
Wherein, large main shaft (1) circumferentially has the first cambered surface cannelure (18), and the first cambered surface cannelure (18) has away from the side of weighting block (2) the second cambered surface cannelure (19) that diameter is greater than the first cambered surface cannelure (18);
Circle ring device (4) is connected by the annulus cover plate (5) held away from large main shaft (1) by the annulus of two coaxial Different Diameter, two annulus surround circular passage (6), by being respectively arranged with by the spacing great circle band of column (8) of circular passage (6) in the vertical direction away from large spindle end to large major axes orientation in circular passage (6), pretightning force is had in original state and the first Compress Spring (9) be connected with the great circle band of column (8) between the great circle band of column (8) and slip Circular Plate (10), annular boss (11) on the circular passage inwall spacing to slip Circular Plate (10) in the vertical direction, two ends are respectively by slip Circular Plate (10) and the roundlet band of column (13) spacing and the second Compress Spring (12) be connected with the roundlet band of column (13) and the roundlet band of column (13), the roundlet band of column (13) has two states in the first cambered surface cannelure (18) and the second cambered surface cannelure (19).
2. according to claim 1 can the inertial excitation device of Damping resounding, it is characterized in that: described weighting block (2) is by the shaft shoulder on large main shaft (1) and axially spacing at large main shaft (1) of circlip (3) that snap in circlip groove, the correspondence position of the outside wall surface of large main shaft (1) and the internal face of weighting block (2) has keyway, is provided with the flat key of weighting block (2) at large main shaft (1) radial upper limit in keyway.
3. according to claim 2 can the inertial excitation device of Damping resounding, it is characterized in that: described flat key adopts A type flat key.
4. according to claim 1 and 2 can the inertial excitation device of Damping resounding, it is characterized in that: the annulus cover plate (5) that two annulus of described circle ring device (4) are held away from large main shaft (1) by it and being connected through the connecting bolt that annulus cover plate (5) stretches into two two annulus end faces respectively.
5. according to claim 1 or 2 or 3 can the inertial excitation device of Damping resounding, it is characterized in that: the described roundlet band of column (13) diameter and upper first cambered surface cannelure (18) equal diameters of large main shaft (1), circular passage (6) in the vertical direction divides two sections, the channel width that long-range main shaft (1) is held is greater than the passage that nearly large main shaft (1) is held, the roundlet band of column (13) diameter matches with the width of the passage that circular passage (6) nearly large main shaft (1) is held, the width of the passage that the diameter of the great circle band of column (8) is held with circular passage (6) long-range main shaft (1) matches.
6. according to claim 4 can the inertial excitation device of Damping resounding, it is characterized in that: the described roundlet band of column (13) diameter and upper first cambered surface cannelure (18) equal diameters of large main shaft (1), circular passage (6) in the vertical direction divides two sections, the channel width that long-range main shaft (1) is held is greater than the passage that nearly large main shaft (1) is held, the roundlet band of column (13) diameter matches with the width of the passage that circular passage (6) nearly large main shaft (1) is held, the width of the passage that the diameter of the great circle band of column (8) is held with circular passage (6) long-range main shaft (1) matches.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510425321.0A CN105057190B (en) | 2015-07-17 | 2015-07-17 | Can Damping resounding inertial excitation device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510425321.0A CN105057190B (en) | 2015-07-17 | 2015-07-17 | Can Damping resounding inertial excitation device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105057190A true CN105057190A (en) | 2015-11-18 |
| CN105057190B CN105057190B (en) | 2017-08-04 |
Family
ID=54486826
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510425321.0A Expired - Fee Related CN105057190B (en) | 2015-07-17 | 2015-07-17 | Can Damping resounding inertial excitation device |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105057190B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004174473A (en) * | 2002-11-27 | 2004-06-24 | Chowa Kogyo Kk | Control method of vibromotive force, and its control device |
| CN101844131A (en) * | 2010-05-13 | 2010-09-29 | 范文豹 | Vibration exciting method for vibrating machine |
| CN103464536A (en) * | 2013-08-12 | 2013-12-25 | 西北工业大学 | Vibration stress relief formation method and device under elastic deformation condition |
-
2015
- 2015-07-17 CN CN201510425321.0A patent/CN105057190B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004174473A (en) * | 2002-11-27 | 2004-06-24 | Chowa Kogyo Kk | Control method of vibromotive force, and its control device |
| CN101844131A (en) * | 2010-05-13 | 2010-09-29 | 范文豹 | Vibration exciting method for vibrating machine |
| CN103464536A (en) * | 2013-08-12 | 2013-12-25 | 西北工业大学 | Vibration stress relief formation method and device under elastic deformation condition |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105057190B (en) | 2017-08-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101773865B (en) | Multistage eccentric block single barrel vibrating mill | |
| CN203695369U (en) | Sliding type eccentric block | |
| CN101511489B (en) | Centrifuge having a rotor having horizontal axis of rotation | |
| CN104668186A (en) | Solid control vibrating screen | |
| CN103551297A (en) | Amplitude adjustable vibration excitation device | |
| CN201613165U (en) | Multilevel eccentric-block single-cylinder vibration mill | |
| CN101961671A (en) | Variable-rigidity double-mass vibration exciter type super-huge vibration mill | |
| CN202621425U (en) | Double eccentric block type vibration generator | |
| CN205109767U (en) | Vibration ball -milling device | |
| CN105057190A (en) | Inertial excitation device capable of eliminating resonance | |
| CN202851781U (en) | Anti-resonance stepped-type spring oscillation damping device | |
| CN105889398A (en) | Deep hole machining oil conveyor with damping function | |
| CN105437067B (en) | A kind of ultrasonic wave air static pressure spindle device and scribing machine | |
| CN108044695A (en) | A kind of mechanical torsional oscillation platform based on space cam | |
| CN101984270A (en) | Engine balancer | |
| CN207795876U (en) | A kind of elastic shaft bearing | |
| CN108145783A (en) | A kind of mechanical torsional oscillation platform based on synchronous cam | |
| CN211058332U (en) | Slurry vibrator | |
| CN109586616B (en) | Frequency modulation type magnetic coupling piezoelectric generator | |
| CN202845137U (en) | Chaotic vibration mill | |
| CN207680945U (en) | A kind of piezoelectric ceramic vibration source and lathe and industrial robot using the vibration source | |
| CN208556021U (en) | A kind of lathe lathe tool clamp system that can extend lathe tool service life | |
| CN203257970U (en) | Damping device for washing and dehydrating machine | |
| CN109693314A (en) | A kind of ground rotation milling attachment containing exciting agency in axis | |
| CN203695167U (en) | Single-motor breaking device of high-frequency breaking hammer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20170804 Termination date: 20180717 |