CN115143218A - Magneto-rheological tuned particle mass damper - Google Patents
Magneto-rheological tuned particle mass damper Download PDFInfo
- Publication number
- CN115143218A CN115143218A CN202210764263.4A CN202210764263A CN115143218A CN 115143218 A CN115143218 A CN 115143218A CN 202210764263 A CN202210764263 A CN 202210764263A CN 115143218 A CN115143218 A CN 115143218A
- Authority
- CN
- China
- Prior art keywords
- piston head
- outer cylinder
- mass damper
- end cover
- cylinder barrel
- 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.)
- Pending
Links
- 239000002245 particle Substances 0.000 title claims abstract description 34
- 238000013016 damping Methods 0.000 claims abstract description 21
- 230000000149 penetrating effect Effects 0.000 claims abstract description 4
- 230000005284 excitation Effects 0.000 claims description 5
- 238000000034 method Methods 0.000 claims description 4
- 230000000694 effects Effects 0.000 description 10
- 238000002955 isolation Methods 0.000 description 6
- 239000008188 pellet Substances 0.000 description 6
- 239000000463 material Substances 0.000 description 5
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 4
- 239000002131 composite material Substances 0.000 description 3
- 238000009434 installation Methods 0.000 description 3
- 238000005265 energy consumption Methods 0.000 description 2
- 238000005457 optimization Methods 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000006260 foam Substances 0.000 description 1
- 239000008187 granular material Substances 0.000 description 1
- 238000010030 laminating Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000004745 nonwoven fabric Substances 0.000 description 1
- 230000035945 sensitivity Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000013022 venting Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/01—Vibration-dampers; Shock-absorbers using friction between loose particles, e.g. sand
-
- 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
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/01—Vibration-dampers; Shock-absorbers using friction between loose particles, e.g. sand
- F16F7/015—Vibration-dampers; Shock-absorbers using friction between loose particles, e.g. sand the particles being spherical, cylindrical or the like
-
- 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
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
Abstract
The invention discloses a magneto-rheological tuned particle mass damper, which comprises an outer cylinder barrel, a left end cover component arranged at the left end of the outer cylinder barrel, a right end cover component arranged at the right end of the outer cylinder barrel, a piston rod axially penetrating through the left end cover component and the right end cover component, and a piston head component arranged in the outer cylinder barrel; the piston head assembly is sleeved on the piston rod in an outer mode, and the outer cylinder barrel is provided with a damping adjusting assembly used for adjusting mass damping; the magneto-rheological tuned particle mass damper has the advantages of simple and convenient structure, wide adjustable range and higher controllability, can meet the vibration reduction requirements of working conditions with various vibration characteristics, and solves the problems of non-adjustable parameters, poor working condition adaptability and unstable performance of the traditional tuned mass damper.
Description
Technical Field
The invention relates to the field of magneto-rheological vibration isolation, in particular to a magneto-rheological tuned particle mass damper.
Background
The damper capable of realizing the vibration isolation effect without supporting mainly comprises a tuned mass damper and a particle damper. The existing traditional tuned mass damper can achieve a good effect on a specific frequency band, and the basic principle is that vibration energy of a main system is transferred to a mass unit of the tuned mass damper to realize vibration reduction of the main system. The particle damper needs to provide a limited closed space in a vibration system and fill particles in the limited closed space, and the basic vibration damping principle is that mechanical energy is converted into heat energy for dissipation by utilizing friction and collision between particles and between the particles and the inner wall of a cavity, so that a better vibration isolation effect is achieved. The two dampers belong to the category of passive dampers, are single in adaptation working condition and difficult to realize vibration isolation in the broadband field.
In order to solve the problems of non-adjustable parameters and poor working condition adaptability of the conventional passive tuned mass damper and the problem of unstable performance caused by mass sensitivity of the conventional passive tuned mass damper, a new magnetorheological damper is required to solve the problems.
Disclosure of Invention
In view of this, the magnetorheological tuned particle mass damper of the technical scheme has a simple and convenient structure, a wide adjustable range and high controllability, can meet the vibration reduction requirements of working conditions with various vibration characteristics, and overcomes the problems of non-adjustable parameters, poor working condition adaptability and unstable performance of the traditional tuned mass damper.
A magneto-rheological tuned particle mass damper comprises an outer cylinder barrel, a left end cover assembly arranged at the left end of the outer cylinder barrel, a right end cover assembly arranged at the right end of the outer cylinder barrel, a piston rod axially penetrating through the left end cover assembly and the right end cover assembly, and a piston head assembly arranged in the outer cylinder barrel; the piston head assembly is sleeved on the piston rod in an outer mode, and the outer cylinder barrel is provided with a damping adjusting assembly used for adjusting mass damping.
Further, the piston head assembly comprises a piston head arranged on the piston rod, an excitation coil wound on the piston head and a clamp spring arranged on the piston rod and used for axially limiting the piston head; an annular channel is formed between the piston head and the outer cylinder.
Further, the annular mounting groove that is used for installing excitation coil is seted up to piston head circumferential direction, all be provided with the spring between piston head and the left end lid subassembly and between piston head and the right-hand member lid.
Furthermore, a plurality of mounting holes for mounting the damping adjusting assembly are formed in the circumferential direction of the outer cylinder barrel.
Further, the damping adjustment assembly is including setting up the granule bobble and the axial that set up in the mounting hole and wear to establish and fixedly set up the quality pole in the mounting hole, the quality pole tip is provided with and is used for locking the locking piece in left end cover subassembly tip and right-hand member lid subassembly tip with the quality pole.
Further, the left end cover assembly and the right end cover assembly are identical in structure, the left end cover assembly comprises a guide seat and a flange plate arranged on the guide seat, the guide seat is fixedly connected with the flange plate, and the end face of the flange plate is attached to the end face of the outer cylinder barrel.
Furthermore, the guide holder is formed with the direction installation department that is used for installing the spring along axial direction, the spring overcoat is on the direction installation department.
Furthermore, the piston rod is provided with an exhaust hole.
The invention has the beneficial effects that:
the magneto-rheological tuned particle mass damper has the advantages of simple and convenient structure, wide adjustable range and higher controllability, can meet the vibration reduction requirements of working conditions with various vibration characteristics, and solves the problems of non-adjustable parameters, poor working condition adaptability and unstable performance of the traditional tuned mass damper. Adopting a magnetorheological composite material; the material has good anti-settling property, durability and magneto-rheological effect adjusting range, and improves the output damping characteristic of the damper. The usage amount of the magnetorheological material is greatly reduced, the cost is reduced, and an additional sealing device is not needed. By utilizing the collision energy dissipation effect of the small particle balls in the through holes in the outer cylinder part of the damper, the energy dissipation effect of the magnetorheological damper can be improved, and the high-efficiency vibration isolation frequency band of the damper is widened. The damper parameters are selected based on parameter optimization. Considering the existence variability of the spring stiffness, the mass part can be adjusted by adding a screw rod on the circular hole of the outer cylinder of the damper, increasing particles and the like, so that the damper is suitable for different vibration working conditions quickly.
Drawings
The invention is further described below with reference to the following figures and examples:
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a side view of the present invention;
FIG. 3 is a second structural diagram of the present invention.
Detailed Description
FIG. 1 is a schematic view of the overall structure of the present invention; FIG. 2 is a side view of the present invention; FIG. 3 is a second schematic structural view of the present invention; as shown in the figure, the magneto-rheological tuned particle mass damper comprises an outer cylinder barrel 5, a left end cover assembly arranged at the left end of the outer cylinder barrel 5, a right end cover assembly arranged at the right end of the outer cylinder barrel 5, a piston rod 8 axially penetrating through the left end cover assembly and the right end cover assembly, and a piston head assembly arranged in the outer cylinder barrel 5; the piston head assembly is sleeved on the piston rod 8 in an outer sleeve mode, and the outer cylinder barrel 5 is provided with a damping adjusting assembly used for adjusting mass damping; the magneto-rheological tuned particle mass damper has the advantages of simple and convenient structure, wide adjustable range and higher controllability, can meet the vibration reduction requirements of working conditions with various vibration characteristics, and solves the problems of non-adjustable parameters, poor working condition adaptability and unstable performance of the traditional tuned mass damper. Adopting a magnetorheological composite material; the material has good anti-settling property, durability and magneto-rheological effect adjusting range, and improves the output damping characteristic of the damper. The usage amount of the magnetorheological material is greatly reduced, the cost is reduced, and an additional sealing device is not needed. By utilizing the collision energy dissipation function of the small particles inside the through holes in the outer cylinder part of the damper, the energy dissipation effect of the magnetorheological damper can be improved, and the high-efficiency vibration isolation frequency band of the damper is widened. The damper parameters are selected based on parameter optimization. Considering the existence variability of the spring stiffness, the mass part can be adjusted by adding a screw rod on the circular hole of the outer cylinder of the damper, increasing particles and the like, so that the damper is fast suitable for different vibration working conditions.
In this embodiment, the piston head assembly includes a piston head 6 mounted on the piston rod 8, an excitation coil wound on the piston head 6, and a clamp spring 10 mounted on the piston rod 8 for axially limiting the piston head 6; an annular channel is formed between the piston head 6 and the outer cylinder 5. The piston rod 8 can slide relative to the left end cover assembly and the right end cover assembly, a piston rod ring groove used for installing a clamp spring 10 is formed in the piston rod, the clamp springs 10 are arranged at the left end and the right end of the piston head 6 and used for limiting the piston head, an annular channel is formed between the piston head 6 and the outer cylinder barrel 5, magnetorheological composite materials (such as magnetorheological non-woven fabrics and magnetorheological foam) are arranged in the circumferential direction of the piston head, the piston rod moves to drive the piston head 6 to move, magnetorheological vibration damping movement is achieved, and mechanical energy is converted into heat energy to be dissipated through a damping effect between the piston head of the magnetorheological damper and the outer cylinder barrel.
In this embodiment, the piston head 6 is provided with an annular mounting groove in the circumferential direction for mounting the excitation coil, and springs 7 are respectively arranged between the piston head 6 and the left end cover assembly and between the piston head and the right end cover. The annular mounting groove is formed in the circumferential direction of the piston head and used for winding the magnet exciting coil, the springs 7 are arranged at the left end and the right end of the piston head, and the piston head returns after vibration damping movement is finished.
In this embodiment, a plurality of mounting holes 12 for mounting the damping adjusting assembly are formed in the outer cylinder 5 in the circumferential direction. A plurality of mounting holes 12 are uniformly arranged in the same circumferential direction of the outer cylinder barrel 5 and used for adjusting and mounting the damping adjusting component.
In this embodiment, the damping adjustment assembly includes the pellet 11 disposed in the mounting hole 12 and the mass rod 51 axially disposed through and fixedly disposed in the mounting hole, and a locking member for locking the mass rod 51 to the end of the left end cover assembly and the end of the right end cover assembly is disposed at the end of the mass rod 51. The small granular balls 11 can be made of materials which can consume energy through collision and friction, such as steel balls and gravels; the end part of the mass rod 51 is processed to form a thread structure, the mass rod is matched with a locking piece to be locked, the locking piece adopts a nut 53 structure, and a gasket 52 is further arranged between the nut 53 and the end cover assembly. The particle pellet 11 collides with the energy consumption part, the mechanical energy in the vibration process is converted into heat energy by utilizing mutual collision of the particle pellets in the outer cylinder barrel in the vibration process and friction and collision of the particles and the mounting hole 12, and the mechanical energy is dissipated, the particle pellets 11 and the mass rod 51 are specifically arranged and can be selectively mounted according to actual conditions, and a particle pellet mode can be adopted, as shown in fig. 3, the particle pellets can be used for providing mass for the damper and can also realize the energy consumption effect in the vibration process.
In this embodiment, left end cover subassembly and right-hand member lid subassembly structure are the same, left end cover subassembly includes guide holder 9 and installs ring flange 4 on guide holder 9, guide holder 9 sets up with ring flange 4 fixed connection, the ring flange terminal surface is installed with the laminating of outer cylinder terminal surface. The end face of the flange plate 4 is attached to the guide seat 9 and is connected and locked through the bolt 2.
In this embodiment, the guide seat 9 is formed with a guide mounting portion along the axial direction for mounting the spring 7, and the spring 9 is sleeved on the guide mounting portion. The guide mounting portion facilitates the mounting of the spring 7 in the housing. Two ends of the piston rod are respectively arranged on the vibration bearing 1 and are used for vibration reduction and energy absorption.
In this embodiment, the piston rod 8 is provided with an air vent 81. The vent hole 81 is provided for venting air and for wire installation.
Finally, the above embodiments are only for illustrating the technical solutions of the present invention and not for limiting, although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that modifications or equivalent substitutions may be made to the technical solutions of the present invention without departing from the spirit and scope of the technical solutions of the present invention, and all of them should be covered in the claims of the present invention.
Claims (8)
1. A magneto-rheological tuned particle mass damper, the method is characterized in that: the piston rod assembly is arranged in the outer cylinder barrel; the piston head assembly is sleeved outside the piston rod, and the outer cylinder barrel is provided with a damping adjusting assembly used for adjusting mass damping.
2. The magnetorheological tuned particle mass damper according to claim 1, wherein: the piston head assembly comprises a piston head arranged on the piston rod, a magnet exciting coil wound on the piston head and a clamp spring arranged on the piston rod and used for axially limiting the piston head; an annular channel is formed between the piston head and the outer cylinder.
3. The magnetorheological tuned particle mass damper according to claim 2, wherein: the annular mounting groove that is used for installing excitation coil is seted up to piston head circumferential direction, all be provided with the spring between piston head and the left end lid subassembly and between piston head and the right-hand member lid.
4. The magnetorheological tuned particle mass damper according to claim 1, wherein: and a plurality of mounting holes for mounting the damping adjusting assembly are formed in the circumferential direction of the outer cylinder barrel.
5. The magnetorheological tuned particle mass damper according to claim 4, wherein: the damping adjustment assembly comprises a particle ball arranged in the mounting hole and a mass rod axially arranged in the mounting hole in a penetrating mode, and the end portion of the mass rod is provided with a locking piece used for locking the mass rod in the end portion of the left end cover assembly and the end portion of the right end cover assembly.
6. The magnetorheological tuned particle mass damper according to claim 5, wherein: the left end cover assembly and the right end cover assembly are identical in structure, the left end cover assembly comprises a guide seat and a flange plate arranged on the guide seat, the guide seat is fixedly connected with the flange plate, and the end face of the flange plate is attached to the end face of the outer cylinder barrel.
7. The magnetorheological tuned particle mass damper according to claim 6, wherein: the guide seat is formed with a guide mounting part for mounting the spring along the axial direction, the spring is sleeved on the guide mounting portion.
8. The magnetorheological tuned particle mass damper according to claim 7, wherein: the piston rod is provided with an exhaust hole.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210764263.4A CN115143218A (en) | 2022-06-30 | 2022-06-30 | Magneto-rheological tuned particle mass damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210764263.4A CN115143218A (en) | 2022-06-30 | 2022-06-30 | Magneto-rheological tuned particle mass damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN115143218A true CN115143218A (en) | 2022-10-04 |
Family
ID=83410780
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210764263.4A Pending CN115143218A (en) | 2022-06-30 | 2022-06-30 | Magneto-rheological tuned particle mass damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115143218A (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2806880Y (en) * | 2005-07-13 | 2006-08-16 | 宁波杉工结构监测与控制工程中心有限公司 | Double-rod clearance type damping liquid and spring composite vibration damper |
| CN101319699A (en) * | 2008-07-11 | 2008-12-10 | 重庆大学 | Magneto-rheological fluid vibration damper with ring-shaped external magnetic field generator |
| CN101839299A (en) * | 2010-02-09 | 2010-09-22 | 谭晓婧 | Two-dimensional magnetorheological damper |
| WO2010117069A1 (en) * | 2009-04-09 | 2010-10-14 | 株式会社神戸製鋼所 | Vibration damping structure |
| CN102644691A (en) * | 2012-05-21 | 2012-08-22 | 上海应用技术学院 | Double-access foam metal magneto-rheological fluid damper |
| CN108050337A (en) * | 2017-11-06 | 2018-05-18 | 成都飞机工业（集团）有限责任公司 | For the alloyed aluminium variable chamber particles-impact damper of pipeline vibration damping |
| JP6343060B1 (en) * | 2017-04-19 | 2018-06-13 | Ｋｙｂ株式会社 | Damper with power generation function |
| CN108591343A (en) * | 2018-04-17 | 2018-09-28 | 安徽卓特信息技术有限公司 | A kind of externally-wound type MR damper of cylinder barrel positioning |
| WO2019172328A1 (en) * | 2018-03-07 | 2019-09-12 | Ntn株式会社 | Bearing vibration damping device |
| CN212297414U (en) * | 2020-06-12 | 2021-01-05 | 华域汽车电动系统有限公司 | Dynamic balance plate with vibration damping function |
| CN214698935U (en) * | 2021-05-31 | 2021-11-12 | 镇江知名建设工程有限公司 | Shock insulation damper with liquid and particles |
| US20210381579A1 (en) * | 2020-06-03 | 2021-12-09 | National Central University | Dynamic balancing apparatus |
-
2022
- 2022-06-30 CN CN202210764263.4A patent/CN115143218A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2806880Y (en) * | 2005-07-13 | 2006-08-16 | 宁波杉工结构监测与控制工程中心有限公司 | Double-rod clearance type damping liquid and spring composite vibration damper |
| CN101319699A (en) * | 2008-07-11 | 2008-12-10 | 重庆大学 | Magneto-rheological fluid vibration damper with ring-shaped external magnetic field generator |
| WO2010117069A1 (en) * | 2009-04-09 | 2010-10-14 | 株式会社神戸製鋼所 | Vibration damping structure |
| CN101839299A (en) * | 2010-02-09 | 2010-09-22 | 谭晓婧 | Two-dimensional magnetorheological damper |
| CN102644691A (en) * | 2012-05-21 | 2012-08-22 | 上海应用技术学院 | Double-access foam metal magneto-rheological fluid damper |
| JP6343060B1 (en) * | 2017-04-19 | 2018-06-13 | Ｋｙｂ株式会社 | Damper with power generation function |
| CN108050337A (en) * | 2017-11-06 | 2018-05-18 | 成都飞机工业（集团）有限责任公司 | For the alloyed aluminium variable chamber particles-impact damper of pipeline vibration damping |
| WO2019172328A1 (en) * | 2018-03-07 | 2019-09-12 | Ntn株式会社 | Bearing vibration damping device |
| CN108591343A (en) * | 2018-04-17 | 2018-09-28 | 安徽卓特信息技术有限公司 | A kind of externally-wound type MR damper of cylinder barrel positioning |
| US20210381579A1 (en) * | 2020-06-03 | 2021-12-09 | National Central University | Dynamic balancing apparatus |
| CN212297414U (en) * | 2020-06-12 | 2021-01-05 | 华域汽车电动系统有限公司 | Dynamic balance plate with vibration damping function |
| CN214698935U (en) * | 2021-05-31 | 2021-11-12 | 镇江知名建设工程有限公司 | Shock insulation damper with liquid and particles |
Non-Patent Citations (1)
| Title |
|---|
| 董小闵;余淼;廖昌荣;陈伟民;: "冲击载荷下磁流变变刚度变阻尼缓冲系统减振控制", 农业机械学报, vol. 1, no. 03, pages 157 - 30 * |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10690215B2 (en) | Damper with electro-magnetic actuator | |
| US9086111B2 (en) | Valve assembly of shock absorber | |
| US4477061A (en) | Strut type suspension | |
| CN104500641B (en) | A kind of birotor self-powered amortisseur based on magnetic rheology elastic body | |
| CN107956839B (en) | A kind of compound Adjustable transmission system torsional vibration damper with particle damping and electromagnetic damping | |
| CN110701239B (en) | Vibration damping and buffering integrated device | |
| CN107606041A (en) | The type hybrid damper that MR damper and eddy current damper combine | |
| CN110043598B (en) | Active vibration isolator based on compounding of magnetorheological cement and metal rubber | |
| CN109737163B (en) | Moving coil type actuator for engine active suspension | |
| CN110425241A (en) | A kind of active engine mount of moving-magnetic type electromagnetic actuator actuation | |
| CN114101801B (en) | Damping vibration attenuation cutter | |
| CN115143218A (en) | Magneto-rheological tuned particle mass damper | |
| EP0819866B1 (en) | Vibration damper having oscillating force generating means | |
| CN204403256U (en) | A kind of double rotor self-powered vibration damper based on magnetic rheology elastic body | |
| CN108343694A (en) | A kind of mixed type dynamic vibration absorber using bicyclic concatenation type permanent magnet | |
| CN214036664U (en) | Frequency-adjustable damping easily-adjustable electric magnetic dynamic vibration absorber | |
| CN217502423U (en) | Piston assembly of magneto-rheological single-cylinder shock absorber for automobile | |
| CN114838082A (en) | Multistage variable damping variable stiffness shock absorber based on magnetorheological material | |
| CN113352829A (en) | Traveller assembly and vehicle | |
| CN208858811U (en) | A kind of electromagnetic fan clutch with spring shock absorption mechanism | |
| CN215928214U (en) | Magnetorheological fluid dynamic vibration absorber using double pump wheels | |
| CN205956283U (en) | A damper for motorcycle damper cylinder | |
| CN116241597A (en) | Built-in compensation type integrated magneto-rheological damper | |
| CN216805103U (en) | Vibration damping structure for engine | |
| CN116044950A (en) | Motorcycle shock absorber |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |