CN113494559A - Metal vibration isolator with damping force proportional to vibration displacement - Google Patents
Metal vibration isolator with damping force proportional to vibration displacement Download PDFInfo
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- CN113494559A CN113494559A CN202110848067.0A CN202110848067A CN113494559A CN 113494559 A CN113494559 A CN 113494559A CN 202110848067 A CN202110848067 A CN 202110848067A CN 113494559 A CN113494559 A CN 113494559A
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- spring
- rotating shaft
- descending
- ascending
- uplink
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/022—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using dampers and springs in combination
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/04—Friction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2238/00—Type of springs or dampers
- F16F2238/02—Springs
- F16F2238/024—Springs torsional
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2238/00—Type of springs or dampers
- F16F2238/02—Springs
- F16F2238/026—Springs wound- or coil-like
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Springs (AREA)
Abstract
The invention discloses a metal vibration isolator with damping force proportional to vibration displacement, and belongs to the field of variable damping vibration isolators. The vibration isolation device comprises a shell, a bottom plate, an upper cover, a lifting column and a vibration isolation platform, wherein the lower end of the lifting column is fixedly provided with a bilateral dislocation subsection rack, the left side and the right side of the bilateral dislocation subsection rack are symmetrically provided with an uplink rotating shaft and a downlink rotating shaft along the horizontal direction, the uplink rotating shaft is fixedly provided with an uplink gear and an uplink winding wheel, the downlink rotating shaft is fixedly provided with a downlink gear and a downlink winding wheel, the bottom plate is provided with a downlink spiral spring, and the upper cover is provided with an uplink spiral spring; the upper rotating shaft and the lower rotating shaft are both provided with conical springs, so that the inner diameter change trends of the conical springs are different when the steering is different. The invention is a metal vibration isolator which has simple and reasonable structure, generates variable damping force by depending on friction, and the damping force is in direct proportion to vibration displacement.
Description
Technical Field
The invention mainly relates to the field of variable damping vibration isolators, in particular to a metal vibration isolator with damping force in direct proportion to vibration displacement.
Background
Metal vibration isolators are widely used because of their good stiffness characteristics. The prior art metal vibration isolators typically have a low damping force with no apparent regularity of variation in the damping force, and this damping characteristic is of no value for shock isolation. Therefore, the metal vibration isolator with the damping force regularly changing along with the vibration displacement is designed to have very important significance.
Disclosure of Invention
The technical problems to be solved by the invention are as follows: aiming at the technical problems in the prior art, the invention provides the metal vibration isolator which is simple and reasonable in structure, generates variable damping force by means of friction, and the damping force is in direct proportion to vibration displacement.
In order to solve the problems, the solution proposed by the invention is as follows: the metal vibration isolator with damping force proportional to vibration displacement includes one casing, one bottom board and one upper cover set separately on the upper and lower ends of the casing, one elevating column penetrating the upper cover for free elevating, and one vibration isolating platform fixed on the elevating column.
The lower extreme of lift post is fixed to be installed two side dislocation segmentation racks, the ascending pivot and the descending pivot that the horizontal direction symmetry was installed along the two side dislocation segmentation rack left and right sides, go up the fixed gear and go up the reel of having installed in the pivot, down fixed gear and the descending reel of having installed in the pivot, the bottom plate facial make-up is equipped with down coil spring, the spiral spring that goes up is installed on the upper cover.
The lower section of the left side of the bilateral segmentation rack is provided with an ascending tooth in meshing transmission with the ascending gear, the upper section of the right side of the bilateral segmentation rack is provided with a descending tooth in meshing transmission with the descending gear, the middle of the bilateral segmentation rack is provided with a sliding chute, and the sliding chute is internally provided with the rectangular guide rod with the cross section size matched with the sliding chute in a sliding manner.
The rectangular guide rod is horizontally arranged, two ends of the rectangular guide rod are fixedly connected with the front side face and the rear side face of the shell, the downlink rotating shaft and the uplink rotating shaft are parallel to the rectangular guide rod, and two ends of the rectangular guide rod are rotatably arranged on the shell.
The upper end of the upward spiral spring is connected with the upper cover, the lower end of the upward spiral spring is connected with one end of the upward traction rope, and the other end of the upward traction rope is wound on the upward reel; the lower end of the downward spiral spring is connected with the bottom plate, the upper end of the downward spiral spring is connected with one end of the downward traction rope, and the other end of the downward traction rope is wound on the downward reel.
The descending conical spring A and the descending conical spring B which are identical in structure and opposite in rotation direction are respectively sleeved at two ends of the descending rotating shaft, the large-diameter end of each spring is connected with the shell, the small-diameter end of each spring is free, and the inner diameter of each small-diameter end of each spring is equal to the outer diameter of the descending rotating shaft; the ascending conical spring A and the ascending conical spring B which are identical in structure and opposite in rotating direction are sleeved at two ends of the ascending rotating shaft, the large-diameter end of the spring is connected with the shell, the small-diameter end of the spring is free, and the inner diameter of the small-diameter end of the spring is equal to the outer diameter of the ascending rotating shaft.
When the vibration isolation instrument is mounted on the vibration isolation platform, the bilateral staggered sectional racks are just positioned at the balance position, when the bilateral staggered sectional racks move downwards away from the balance position, the inner diameters of the descending conical helical spring A and the descending conical spring B are gradually reduced, and the inner diameters of the ascending conical spring A and the ascending conical spring B are unchanged; when the bilateral staggered sectional racks move upwards away from the balance position, the inner diameters of the ascending conical spring A and the ascending conical spring B are gradually reduced, and the inner diameters of the descending conical helical spring A and the descending conical spring B are unchanged.
Compared with the prior art, the invention has the following advantages and beneficial effects: the metal vibration isolator with the damping force proportional to the vibration displacement is provided with the upper rotating shaft and the lower rotating shaft, and the upper rotating shaft and the lower rotating shaft are both provided with the conical springs, so that the inner diameter change trends of the conical springs are different when the steering directions are different, the friction force between the conical springs and the upper rotating shaft or the lower rotating shaft is further changed, and the effect that the damping force is proportional to the vibration displacement is achieved. Therefore, the metal vibration isolator has a simple and reasonable structure, generates variable damping force by means of friction, and has the damping force proportional to vibration displacement.
Drawings
Fig. 1 is a schematic structural diagram of a metal vibration isolator according to the present invention, in which damping force is proportional to vibration displacement.
Fig. 2 is a schematic sectional view taken along line a-a in fig. 1.
In the figure, 11 — bottom plate; 12-a housing; 13-upper cover; 14-a lifting column; 15-vibration isolation platform; 2-bilateral dislocation sectional racks; 21-a chute; 22-upper teeth; 23-descending teeth; 31-a down coil spring; 32-a down haulage rope; 33-a down reel; 34-a down gear; 41-up coil spring; 42-an up-going hauling rope; 43-an up reel; 44-up gear; 5, a rectangular guide rod; 6-a down shaft; 61-descending conical spring A; 62-descending conical spring B; 7, an ascending rotating shaft; 71-upward conical spring a; 72-upward going conical spring B.
Detailed Description
The invention will be described in further detail below with reference to the accompanying drawings and specific embodiments.
Referring to fig. 1 and 2, the metal vibration isolator with damping force proportional to vibration displacement according to the present invention includes a housing 12, a bottom plate 11 and an upper cover 13 respectively installed at upper and lower ends of the housing 12, a lifting column 14 passing through the upper cover 13 to be freely lifted, and a vibration isolation platform 15 fixedly installed at an upper end of the lifting column 14.
The lower end of the lifting column 14 is fixedly provided with a double-side dislocation subsection rack 2, the left side and the right side of the double-side dislocation subsection rack 2 are symmetrically provided with an upper rotating shaft 7 and a lower rotating shaft 6 along the horizontal direction, the upper rotating shaft 7 is fixedly provided with an upper gear 44 and an upper reel 43, the lower rotating shaft 6 is fixedly provided with a lower gear 34 and a lower reel 33, the bottom plate 11 is provided with a lower spiral spring 31, and the upper cover 13 is provided with an upper spiral spring 41.
The left lower section of the bilateral segmented rack 2 is provided with an upper tooth 22 in meshing transmission with an upper gear 44, the right upper section is provided with a lower tooth 23 in meshing transmission with a lower gear 34, and the middle part is provided with a chute 21 matched with the cross section size of the rectangular guide rod 5; the rectangular guide bar 5 slides through the slide slot 21.
The rectangular guide rod 5 is arranged along the horizontal direction, two ends of the rectangular guide rod are fixedly connected with the front side surface and the rear side surface of the shell 12, the downward rotating shaft 6 and the upward rotating shaft 7 are parallel to the rectangular guide rod 5, and two ends of the rectangular guide rod are rotatably arranged on the shell 12.
The upper end of the up coil spring 41 is connected with the upper cover 13, the lower end is connected with one end of an up traction rope 42, and the other end of the up traction rope 42 is wound on an up reel 43; the lower end of the down coil spring 31 is connected to the base plate 11, the upper end thereof is connected to one end of a down traction rope 32, and the other end of the down traction rope 32 is wound on a down reel 33. The upper coil spring 41 and the lower coil spring 31 have the same stiffness, so that the entire system has a symmetrical stiffness characteristic.
The descending conical spring A61 and the descending conical spring B62 which have the same structure and opposite rotating directions are respectively sleeved at two ends of the descending rotating shaft 6, the large-diameter end of the spring is connected with the shell 12, and the small-diameter end of the spring is free; an upward conical spring A71 and an upward conical spring B72 which have the same structure and opposite rotating directions are respectively sleeved at two ends of the upward rotating shaft 7, the large-diameter end of the spring is connected with the shell 12, and the small-diameter end is free. The inner diameter of the small end of the descending conical spring A61 is equal to the outer diameter of the descending rotary shaft 6, and the inner diameter of the small end of the ascending conical spring A71 is equal to the outer diameter of the ascending rotary shaft 7.
When the bilateral dislocation segmented rack 2 moves downwards away from the balance position, the average inner diameters of the descending conical spiral spring A61 and the descending conical spring B62 are gradually reduced, and the inner diameters of the ascending conical spring A71 and the ascending conical spring B72 are unchanged; when the bilateral staggered sectional rack 2 moves upwards away from the balance position, the average inner diameters of the ascending conical spring A71 and the ascending conical spring B72 are gradually reduced, and the inner diameters of the descending conical spiral spring A61 and the descending conical spring B62 are unchanged.
The working principle is as follows: when the bilateral dislocation segmented rack 2 moves downwards below a balance position, the descending teeth 23 are in meshed transmission with the descending gear 34, the descending reel 33 winds the descending traction rope 32, and the descending spiral spring 31 is pulled; when the bilateral staggered sectional rack 2 moves upwards above the balance position, the ascending teeth 22 are meshed with the ascending gear 44 for transmission, the ascending reel 33 winds the ascending traction rope 42, and the ascending helical spring 41 is pulled.
In the process that the bilateral staggered sectional rack 2 moves downwards away from the balance position, when the descending reel 33 winds the descending traction rope 32, the descending rotating shaft 6 rotates positively to drive the descending conical spiral spring A61 and the descending conical spring B62 to wind the descending rotating shaft 6 positively, the average inner diameter of the springs is gradually reduced, and the damping force is gradually increased; in the process that the bilateral staggered sectional rack 2 moves upwards towards the balance position, when the descending reel 33 releases the descending traction rope 32, the descending rotating shaft 6 rotates reversely to drive the descending conical spiral spring A61 and the descending conical spring B62 to reversely loosen the rotating shaft, the average inner diameter of the springs is gradually increased, and the damping force is gradually reduced. In the whole process, the rotating speed of the descending rotating shaft 6 in the normal range enables no relative sliding to occur between the descending rotating shaft 6 and the small-diameter ends of the descending conical spiral spring A61 and the descending conical spring B62, and the damping force is composed of winding force; if the rotating speed of the descending rotating shaft 6 is too high, a certain relative sliding occurs between the descending rotating shaft 6 and the descending conical spiral spring A61 and the descending conical spring B62, but the friction force is still in inverse proportion to the average inner diameter of the springs, and the damping force consists of winding force and friction force; the small-diameter end is free, so that the phenomenon of blocking after the descending conical spiral spring A61 and the descending conical spring B62 are completely wound on the descending rotating shaft 6 is effectively prevented, and the influence on the rigidity property of the system due to the coupling of the winding force and the rigidity of the system caused by the overhigh rotating speed of the descending rotating shaft 6 is effectively avoided.
In the process that the bilateral staggered sectional rack 2 moves upwards away from the balance position, when the ascending reel 33 winds the ascending traction rope 42, the ascending rotating shaft 7 rotates positively to drive the ascending conical spring A71 and the ascending conical spring B72 to wind the ascending rotating shaft 7 positively, the average inner diameter of the springs is gradually reduced, and the damping force is gradually increased; in the process that the bilateral staggered sectional rack 2 returns to the balance position downwards, when the ascending reel 33 releases the ascending traction rope 42, the ascending rotating shaft 7 rotates reversely to drive the ascending conical spring A71 and the ascending conical spring B72 to reversely loosen the rotating shaft, the average inner diameter of the springs is gradually increased, and the damping force is gradually reduced. The damping force during the entire process is similar to the damping force during the process in which the down reel 33 winds or releases the down traction rope 32.
After the vibration isolation instrument is installed on the vibration isolation platform 15, the bilateral staggered sectional rack 2 is just located at a balance position, namely, a central connecting line of the uplink rotating shaft 7 and the downlink rotating shaft 6 passes through a junction of the uplink teeth 22 and the downlink teeth 23. A first movement phase: when the vibration isolation platform 15 moves downwards away from the balance position, the descending teeth 23 of the bilateral dislocation segmented rack 2 are meshed to drive the descending gear 34 to rotate, the descending reel 33 winds the descending traction rope 32, the rigidity of the descending spiral spring 31 is equal to that of the system, and the descending rotating shaft 6 rotates in the positive direction to enable the inner diameters of the descending conical spring A61 and the descending conical spring B62 to be gradually reduced, namely the damping force is gradually increased; and a second motion stage: when the vibration isolation platform 15 moves upwards to return to the balance position, the downward rotating shaft 6 rotates reversely, so that the inner diameters of the downward conical spring A61 and the downward conical spring B62 are gradually increased until the initial inner diameters are restored, namely, the damping force is gradually reduced; in the first movement stage and the second movement stage, the up-going gear 44 and the up-going rotary shaft 7 are not rotated. And a third movement stage: when the vibration isolation platform 15 moves upwards away from the balance position, the ascending teeth 22 of the bilateral dislocation segmented rack 2 are meshed to drive the ascending gear 44, the ascending reel 43 winds the ascending traction rope 42, the rigidity of the system is equal to that of the ascending spiral spring 41, and the forward rotation of the ascending rotating shaft 7 enables the average inner diameters of the ascending conical spring A71 and the ascending conical spring B72 to be gradually reduced, namely the damping force is gradually increased; and a fourth movement stage: when the vibration isolation platform 15 moves downwards to return to the balance position, the reverse rotation of the upper rotating shaft 7 enables the inner diameters of the upper conical spring A71 and the upper conical spring B72 to gradually increase until the initial inner diameters are restored, namely, the damping force is gradually reduced; in the third movement stage and the fourth movement stage, the down gear 34 and the down rotary shaft 6 are not rotated.
The above is only a specific embodiment of the present invention, but the scope of the present invention is not limited thereto, and any changes or substitutions that are not thought of through creative efforts should fall within the scope of the present invention.
Claims (1)
1. A metal vibration isolator with damping force proportional to vibration displacement comprises a shell (12), a bottom plate (11) and an upper cover (13) which are respectively arranged at the upper end and the lower end of the shell (12), a lifting column (14) which penetrates through the upper cover (13) to freely lift, and a vibration isolation platform (15) which is fixedly arranged at the upper end of the lifting column (14); the method is characterized in that:
the lower end of the lifting column (14) is fixedly provided with a bilateral dislocation sectional rack (2), the left side and the right side of the bilateral dislocation sectional rack (2) are symmetrically provided with an uplink rotating shaft (7) and a downlink rotating shaft (6) along the horizontal direction, the uplink rotating shaft (7) is fixedly provided with an uplink gear (44) and an uplink reel (43), the downlink rotating shaft (6) is fixedly provided with a downlink gear (34) and a downlink reel (33), the bottom plate (11) is provided with a downlink spiral spring (31), and the upper cover (13) is provided with an uplink spiral spring (41);
the lower section of the left side of the bilateral segmented rack (2) is provided with an ascending tooth (22) in meshing transmission with the ascending gear (44), the upper section of the right side is provided with a descending tooth (23) in meshing transmission with the descending gear (34), the middle part of the right side is provided with a sliding chute (21), and the sliding chute (21) is internally provided with a rectangular guide rod (5) with the cross section size matched with that of the sliding chute (21) in a sliding manner;
the rectangular guide rod (5) is arranged along the horizontal direction, two ends of the rectangular guide rod are fixedly connected with the front side surface and the rear side surface of the shell (12), the downlink rotating shaft (6) and the uplink rotating shaft (7) are parallel to the rectangular guide rod (5), and two ends of the rectangular guide rod are rotatably arranged on the shell (12);
the upper end of the upward spiral spring (41) is connected with the upper cover (13), the lower end of the upward spiral spring is connected with one end of the upward traction rope (42), and the other end of the upward traction rope (42) is wound on the upward reel (43); the lower end of the downward spiral spring (31) is connected with the bottom plate (11), the upper end of the downward spiral spring is connected with one end of the downward traction rope (32), and the other end of the downward traction rope (32) is wound on the downward reel (33);
a descending conical spring A (61) and a descending conical spring B (62) which have the same structure and opposite rotation directions are respectively sleeved at two ends of the descending rotating shaft (6), the large-diameter end of each spring is connected with the shell (12), the small-diameter end of each spring is free, and the inner diameter of each small-diameter end of each spring is equal to the outer diameter of the descending rotating shaft (6); an ascending conical spring A (71) and an ascending conical spring B (72) which have the same structure and opposite rotation directions are sleeved at two ends of the ascending rotating shaft (7), the large-diameter end of each spring is connected with the shell (12), the small-diameter end of each spring is free, and the inner diameter of each small-diameter end of each spring is equal to the outer diameter of the ascending rotating shaft (7);
when the vibration isolation instrument is mounted on a vibration isolation platform (15), the bilateral dislocation segmented rack (2) is just positioned at a balance position, when the bilateral dislocation segmented rack (2) moves downwards away from the balance position, the inner diameters of the descending conical helical spring A (61) and the descending conical spring B (62) are gradually reduced, and the inner diameters of the ascending conical spring A (71) and the ascending conical spring B (72) are unchanged; when the bilateral dislocation segmented rack (2) moves upwards away from a balance position, the inner diameters of the ascending conical spring A (71) and the ascending conical spring B (72) are gradually reduced, and the inner diameters of the descending conical helical spring A (61) and the descending conical spring B (62) are unchanged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110848067.0A CN113494559B (en) | 2021-07-27 | 2021-07-27 | Metal vibration isolator with damping force proportional to vibration displacement |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110848067.0A CN113494559B (en) | 2021-07-27 | 2021-07-27 | Metal vibration isolator with damping force proportional to vibration displacement |
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| Publication Number | Publication Date |
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| CN113494559A true CN113494559A (en) | 2021-10-12 |
| CN113494559B CN113494559B (en) | 2022-09-16 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202110848067.0A Active CN113494559B (en) | 2021-07-27 | 2021-07-27 | Metal vibration isolator with damping force proportional to vibration displacement |
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| CN (1) | CN113494559B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116201846A (en) * | 2023-05-05 | 2023-06-02 | 溧阳常大技术转移中心有限公司 | Metal vibration isolator with damping force jumping along with displacement |
Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500645A (en) * | 2015-01-06 | 2015-04-08 | 黄加荣 | Kick type vibration absorbing method and kick type vibration absorber |
| CN105546033A (en) * | 2016-02-14 | 2016-05-04 | 苏州辉元变速器科技有限公司 | Torsion damper |
| CN106545610A (en) * | 2016-11-25 | 2017-03-29 | 广东技术师范学院 | A kind of resonance free peak vibration isolator and its damping module |
| CN107849984A (en) * | 2015-09-30 | 2018-03-27 | 株式会社电装 | Torsion spring |
| CN107859705A (en) * | 2017-11-28 | 2018-03-30 | 常州大学 | A kind of full symmetric active frequency modulation damper of tensile and compressive property |
| CN111623074A (en) * | 2020-05-27 | 2020-09-04 | 常州大学 | Fluid-excited fluid-solid mixed damper |
| CN111765197A (en) * | 2020-06-18 | 2020-10-13 | 常州大学 | Shock-resistant large-damping vibration isolator |
| US20200400206A1 (en) * | 2018-03-14 | 2020-12-24 | Gil Zohar | Spring apparatus |
| CN112943584A (en) * | 2021-02-25 | 2021-06-11 | 李博志 | Efficient filtering air compressor and control method thereof |
| CN113074204A (en) * | 2021-03-24 | 2021-07-06 | 常州大学 | Anti-impact ultralow frequency vibration isolator |
-
2021
- 2021-07-27 CN CN202110848067.0A patent/CN113494559B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500645A (en) * | 2015-01-06 | 2015-04-08 | 黄加荣 | Kick type vibration absorbing method and kick type vibration absorber |
| CN107849984A (en) * | 2015-09-30 | 2018-03-27 | 株式会社电装 | Torsion spring |
| US20180238409A1 (en) * | 2015-09-30 | 2018-08-23 | Denso Corporation | Torsion spring |
| CN105546033A (en) * | 2016-02-14 | 2016-05-04 | 苏州辉元变速器科技有限公司 | Torsion damper |
| CN106545610A (en) * | 2016-11-25 | 2017-03-29 | 广东技术师范学院 | A kind of resonance free peak vibration isolator and its damping module |
| CN107859705A (en) * | 2017-11-28 | 2018-03-30 | 常州大学 | A kind of full symmetric active frequency modulation damper of tensile and compressive property |
| US20200400206A1 (en) * | 2018-03-14 | 2020-12-24 | Gil Zohar | Spring apparatus |
| CN111623074A (en) * | 2020-05-27 | 2020-09-04 | 常州大学 | Fluid-excited fluid-solid mixed damper |
| CN111765197A (en) * | 2020-06-18 | 2020-10-13 | 常州大学 | Shock-resistant large-damping vibration isolator |
| CN112943584A (en) * | 2021-02-25 | 2021-06-11 | 李博志 | Efficient filtering air compressor and control method thereof |
| CN113074204A (en) * | 2021-03-24 | 2021-07-06 | 常州大学 | Anti-impact ultralow frequency vibration isolator |
Non-Patent Citations (1)
| Title |
|---|
| 佘凯等: "支承轴承作用下齿轮***动力学分析", 《机械设计与制造》 * |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116201846A (en) * | 2023-05-05 | 2023-06-02 | 溧阳常大技术转移中心有限公司 | Metal vibration isolator with damping force jumping along with displacement |
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| CN113494559B (en) | 2022-09-16 |
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