CN214835226U - Variable additional rigidity viscous damper - Google Patents
Variable additional rigidity viscous damper Download PDFInfo
- Publication number
- CN214835226U CN214835226U CN202120682104.0U CN202120682104U CN214835226U CN 214835226 U CN214835226 U CN 214835226U CN 202120682104 U CN202120682104 U CN 202120682104U CN 214835226 U CN214835226 U CN 214835226U
- Authority
- CN
- China
- Prior art keywords
- piston rod
- damping
- damper
- additional
- cavity
- 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.)
- Active
Links
Images
Landscapes
- Buildings Adapted To Withstand Abnormal External Influences (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The utility model relates to the technical field of dampers, in particular to a viscous damper with variable additional rigidity; the spring group arranged in the additional stiffness cavity does not provide additional stiffness under wind vibration and small earthquake by adopting a staged working mode, so that the structural stiffness is flexible, relatively large displacement is obtained while the earthquake reaction force is reduced, the hysteresis area of the damper is increased, a higher additional damping ratio is obtained, and a higher performance target is obtained while the manufacturing cost is reduced by reducing the steel amount of the main structure by improving the additional damping ratio by utilizing the principle of reinforcing the structure by the additional damping; the main structure is additionally provided with additional rigidity while additional damping is provided under the conditions of medium earthquakes, large earthquakes and rare earthquakes, the interlayer displacement angle of the main structure under the effects of the medium earthquakes, the large earthquakes and the rare earthquakes is controlled, and the main structure is protected from being damaged in the aspects of strength and rigidity improvement.
Description
Technical Field
The patent of the utility model relates to a attenuator technical field, concretely relates to become additional rigidity viscous damper.
Background
The viscous damper is an important shock-absorbing device having characteristics of no additional rigidity and reusability, and thus is widely used. The energy-consuming structure has great energy-consuming capability, can enter an energy-consuming state firstly in strong earthquakes, consumes earthquake energy and attenuates earthquake reaction of the structure, and protects a main structure and a member from being damaged, so that the safety of the structure in the strong earthquakes is ensured. Compared with the traditional anti-seismic structure, the energy dissipation and shock absorption structure adopting the viscous damper can reduce the seismic response by 40-60%.
The viscous damper consists of a cylinder barrel, a piston, a damping hole, viscous fluid damping material, a piston rod and the like, wherein the piston reciprocates in the cylinder barrel. The piston is provided with a damping channel, and the cylinder barrel is filled with viscous fluid damping material.
The energy consumption principle is as follows: when the viscous damper works, along with the reciprocating motion of the piston relative to the cylinder barrel, viscous fluid damping materials flow from the high-pressure cavity to the low-pressure cavity through the damping channel on the piston, and energy is dissipated by overcoming factors such as friction and collision in the process that the viscous fluid damping materials flow through the damping channel in a reciprocating mode.
The theoretical damping force calculation formula of the viscous damper in the prior art is as follows: f ═ C | upsilon-αSign (upsilon), where C is the damping coefficient of the damper, α is the damping index of the damper, and upsilon is the velocity of the displacement point.
The viscous damper in the prior art can only provide additional damping for a main structure under the action of an earthquake, can only play a role in reinforcing the structure, and does not contribute to the rigidity of the structure. For the safety of the main structure under the action of earthquake, some buildings need to consider the strength of the structure and control the displacement of the structure, and if the displacement of the structure is too large and exceeds an allowable displacement value, the main structure is sheared and damaged. And the additional rigidity has a remarkable displacement control effect on the structure under the action of the earthquake.
However, the displacement type shock absorber which can provide additional rigidity for the structure in the existing shock absorbing device does not contribute any or contributes very limited to additional damping of the structure under the condition of a plurality of earthquakes. Meanwhile, the larger the rigidity of the displacement type damper added to the structure is, the larger the seismic force absorbed by the main body structure is, and therefore the rigidity of the energy dissipater added to the main body structure is controlled within a reasonable range.
When the structure is added with rigidity, the aim of reducing the displacement and the damage of the structure in the aspect of improving the rigidity is fulfilled, and meanwhile, a certain amount of damping is added to the structure, so that the earthquake force can be effectively reduced, and the construction cost can be reduced, so that the earthquake-proof performance of the structure is greatly improved in the aspects of improving the strength and the rigidity.
The ideal shock absorbing damper should work in the following way: under wind vibration and small earthquake, additional rigidity is not provided, so that the structure is relatively flexible in rigidity, relatively large displacement is obtained while earthquake reaction force is reduced, the hysteresis area of the damper is increased, a higher additional damping ratio is obtained, and the principle of reinforcing the structure by using the additional damping is utilized to realize the purpose of obtaining higher performance while reducing the steel amount of the main body structure and reducing the manufacturing cost by improving the additional damping ratio; the main structure is additionally provided with additional rigidity while additional damping is provided under the conditions of medium earthquakes, large earthquakes and rare earthquakes, the interlayer displacement angle of the main structure under the effects of the medium earthquakes, the large earthquakes and the rare earthquakes is controlled, and the main structure is protected from being damaged in the aspects of strength and rigidity improvement.
Therefore, it is necessary to provide a variable additional stiffness viscous damper which does not provide additional stiffness under wind vibration and small earthquake to obtain higher additional damping ratio, and provides additional damping and additional stiffness under the action of medium earthquake, large earthquake and rare earthquake to effectively control the displacement angle between the main structure layers to reduce structural damage.
SUMMERY OF THE UTILITY MODEL
The utility model discloses to prior art's not enough, the utility model provides a become additional rigidity viscous damper, the mode that adopts staged work to realize through the spring assembly who sets up in the additional rigidity intracavity does not provide additional rigidity under wind vibration and the slight shock and makes structural rigidity gentler so that obtain relatively great displacement volume when reducing earthquake reaction force, the hysteresis area that increases the attenuator obtains higher additional damping ratio, the principle of utilizing additional damping to the structural reinforcement obtains higher performance target through improving additional damping ratio realization when reducing the steel volume reduction cost of major structure; the main structure is additionally provided with additional rigidity while additional damping is provided under the conditions of medium earthquakes, large earthquakes and rare earthquakes, the interlayer displacement angle of the main structure under the effects of the medium earthquakes, the large earthquakes and the rare earthquakes is controlled, and the main structure is protected from being damaged in the aspects of strength and rigidity improvement.
In order to solve the technical problem, the utility model adopts the following technical scheme:
a variable additional rigidity viscous damper comprises a second lining dividing a cylinder barrel into a damping cavity and an additional rigidity cavity, a first lining arranged at the end of the damping cavity, a first thread pressure pipe and a second thread pressure pipe which are screwed with the cylinder barrel and used for fixing the first lining and the second lining with the cylinder barrel, an ear plate arranged at the end part of the additional rigidity cavity and fixed with the cylinder barrel in a screwing mode, a piston rod penetrating through central inner holes of the first lining and the second lining, a pin head arranged outside the cylinder barrel of the damper and fixed with the end part of the piston rod, a piston fixed on the piston rod and arranged in the damping cavity and dividing the damping cavity into a left chamber and a right chamber, a viscous fluid damping material filled in the damping cavity, wherein the part of the piston rod inserted into the additional rigidity cavity is designed into a stepped shaft structure, and is provided with a shaft head with a diameter smaller than the piston rod and concentric with the piston rod and a stud with a large diameter smaller than the shaft head and concentric with the piston rod, a first spring seat which is sleeved on the shaft head in a hollow way is arranged at the shaft shoulders of the shaft head and the piston rod, the stud and the nut are fixed by screw connection, a second spring seat which is sleeved on the shaft head in a hollow way is arranged at the shoulder part formed by the end part of the nut and the shaft head, a spring group is arranged between the first spring seat and the second spring seat, after the working displacement of the damper exceeds the set displacement A, a multi-stage additional stiffness is provided for the structure through the compression spring group, the interlayer displacement angle of the main structure under the conditions of medium earthquake, large earthquake and rare earthquake is effectively controlled, the effect that the additional stiffness is not provided under the conditions of wind vibration and small earthquake to ensure that the structure has softer stiffness is achieved, so that relatively larger displacement is obtained while the earthquake reaction force is reduced, the hysteresis area of the damper is increased to obtain higher additional damping ratio, and the principle of reinforcing the structure by utilizing the additional damping is utilized to realize the higher performance target while the manufacturing cost is reduced by reducing the steel amount of the main structure and improving the additional damping ratio; the main structure is additionally provided with additional rigidity while additional damping is provided under the conditions of medium earthquakes, large earthquakes and rare earthquakes, the interlayer displacement angle of the main structure under the effects of the medium earthquakes, the large earthquakes and the rare earthquakes is controlled, and the main structure is protected from being damaged in the aspects of strength and rigidity improvement.
Further, the theoretical damping force calculation formula of the variable additional stiffness viscous damper is as follows: when-U0 is less than or equal to U>-F ═ C | υ -αSign(υ)-k(|U|-A)-Fnwhen-A is not more than U not less than A, F is C | upsilon and air count is not more thanαSign (upsilon) when A<When U is more than or equal to U0, F is C | upsilon-αSign(υ)+k(|U|-A)+FnWherein C is the damping coefficient of the damper, alpha is the damping index of the damper, U is the displacement value of the damper, A is the set displacement amplitude of the applied stiffness, upsilon is the velocity of the displacement point, k is the stiffness of the spring group, Fn is the pretightening force of the spring group, and Fn is the pretightening force of the spring group>0, and Fn is 0 if the spring set is not pre-tensioned.
Further, when the piston is at a displacement 0 point, the distance from the end face of the piston close to the first bushing to the end face of the first bushing is the ultimate displacement U0 of the damper, the distance from the end face of the piston close to the second bushing to the end face of the second bushing is the ultimate displacement U0 of the damper, the distance A from the end face of the first spring seat to the end face of the second threaded pressure pipe needs to satisfy 0-A > U0, the distance A from the end face of the second spring seat to the end face of the lug plate needs to satisfy 0-A > U0, and the working stroke of the spring group + the distance A is greater than or equal to the ultimate displacement U0.
Further, the spring group can be a single spring, a plurality of parallel springs, a plurality of series springs and a series-parallel combined spring.
Further, the spring used by the spring group can be a coil spring, a belleville spring, a ring spring or a special-shaped spring.
Further, the first spring seat and the second spring seat are sleeved on the piston rod shaft head in an empty mode.
Further, the spring set may be pre-tensioned or not.
Furthermore, the pretightening force Fn of the spring group can be adjusted by adjusting the left and right positions of the nut.
Further, the spring packs provide additional stiffness during damper extension and also during damper compression.
Further, parameters such as the damping coefficient C, the damping index alpha, the limit displacement U0, the distance A, the rigidity k of the spring group, the pretightening force Fn and the like are given according to the damping use requirement.
Furthermore, the first spring seat and the second spring seat are sleeved on the shaft head of the piston rod in an empty mode and can slide on the shaft head, and compression of the spring group in the damping stretching or compressing process is achieved.
Furthermore, viscous fluid damping materials are filled in the damping cavity, the piston is provided with a damping channel, when the viscous damper works, along with the reciprocating motion of the piston relative to the cylinder barrel, the viscous fluid damping materials flow to the low-pressure cavity from the high-pressure cavity through the damping channel on the piston, and in the process that the viscous fluid damping materials flow through the damping channel in a reciprocating mode, energy is dissipated due to the fact that factors such as friction and collision are overcome.
Furthermore, a guide sleeve and a piston rod seal are arranged at the joint of the first bushing and the piston rod.
Furthermore, a guide sleeve and a piston rod seal are arranged at the joint of the second bushing and the piston rod.
Further, the joint of the first bushing and the second bushing with the cylinder barrel is provided with bushing static seals.
Compared with the prior art, the utility model discloses one of following beneficial effect has at least: the utility model provides a become additional rigidity viscous damper, the mode that adopts working stage by stage through the spring assembly that sets up in the additional rigidity intracavity realizes not providing additional rigidity under wind vibration and little shake and makes structural rigidity gentler so that obtain relatively great displacement volume when reducing earthquake reaction force, increase the hysteresis area of attenuator and obtain higher additional damping ratio, utilize the principle of additional damping to the structural reinforcement to realize obtaining higher performance target when reducing the cost with steel volume reduction cost of major structure through improving additional damping ratio; the main structure is additionally provided with additional rigidity while additional damping is provided under the conditions of medium earthquakes, large earthquakes and rare earthquakes, the interlayer displacement angle of the main structure under the effects of the medium earthquakes, the large earthquakes and the rare earthquakes is controlled, and the main structure is protected from being damaged in the aspects of strength and rigidity improvement.
Drawings
Fig. 1 is a schematic structural view of a variable additional stiffness viscous damper of the present invention;
FIG. 2 is a schematic view of the variable additional stiffness viscous damper according to the present invention in a compressed state;
fig. 3 is a schematic drawing illustrating the operation of the variable additional stiffness viscous damper in a stretching state;
FIG. 4 is a graph of hysteresis without additional stiffness applied by the viscous damper;
FIG. 5 is a graph of additional stiffness applied in stages according to the present invention;
fig. 6 is a graph of hysteresis after additional stiffness is applied in stages.
Fig. 7 is an additional stiffness curve of the present invention for applying a spring band pretension in stages.
Fig. 8 is a graph of hysteresis after applying additional stiffness with pretension of the spring in stages according to the present invention.
Fig. 9 is a schematic structural view of the multi-stage additional stiffness spring set of the present invention.
Fig. 10 is a graph of additional stiffness applied in multiple stages according to the present invention.
Fig. 11 is a hysteresis graph after the multi-stage application of additional stiffness of the present invention.
In the figure: 1-pin head, 2-piston rod, 3-first thread pressure pipe, 4-first bush, 4.1-guide sleeve, 4.2-piston rod seal, 4.3-bush static seal, 5-cylinder, 6-piston, 7-second bush, 8-second thread pressure pipe, 9-first spring seat, 10-spring group, 10.1-first spring, 10.2-second spring, 11-second spring seat, 12-lug plate, 13-nut, 14-viscous fluid damping material.
Detailed Description
As shown in fig. 1 to 11, in order to make the objects, technical solutions and advantages of the present invention more clearly understood, the present invention will be further described in detail with reference to the accompanying drawings and examples. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Example 1
The variable additional rigidity viscous damper comprises a second lining 7, a first lining 4, a first threaded pressure pipe 3, a second threaded pressure pipe 8, an ear plate 12 and a piston rod 2, wherein the second lining 7 divides a cylinder barrel 5 into a damping cavity and an additional rigidity cavity, the first lining 4 is arranged at the end of the damping cavity, the first threaded pressure pipe 3 and the second threaded pressure pipe 8 are in threaded connection with the cylinder barrel 5 and are used for fixing the first lining 4 and the second lining 7 with the cylinder barrel 5, the ear plate 12 is arranged at the end part of the additional rigidity cavity and is fixed with the cylinder barrel 5 in a threaded connection mode, the piston rod 2 penetrates through a central inner hole of the first lining 4 and the second lining 7, one end of the piston rod 2 penetrates through the first lining 4 to extend out of the damping cavity to be fixed with a pin head 1, the other end of the piston rod 2 penetrates through the second lining 7 to be inserted into the additional rigidity cavity, a piston 6 is fixed on the piston rod 2, the damping cavity is divided into a left cavity and a right cavity by the piston 6, the part, which is designed into a stepped shaft structure, and the end of the piston rod 2 is provided with a shaft head and a large diameter smaller than the piston rod and keeps concentric with the piston rod A stud which is smaller than the shaft head and is concentric with the piston rod 2, a first spring seat 9 which is sleeved on the shaft head is arranged at the shaft shoulders of the shaft head and the piston rod 2, the stud adopts a screw connection mode to fix the nut 13 at the end part of the piston rod 2, the shoulder part formed by the end surface of the nut 13 and the shaft head is provided with a second spring seat 11 which is sleeved on the shaft head in a hollow way, a spiral spring 10 is arranged between the first spring seat 9 and the second spring seat 11, when the damper is at a displacement 0 point, the distance A is kept between the end surface of the first spring seat 9 close to the second threaded pressure pipe 8 and the end surface of the second threaded pressure pipe 8, the end face of the second spring seat 11 close to the lug plate 12 keeps the same distance A to the end face of the lug plate 12, a guide sleeve 4.1 and a piston rod seal 4.2 are arranged at the joint of the first bushing 4 and the second bushing 7 with the piston rod 2, and a bushing static seal 4.3 is arranged at the joint of the first bushing 4 and the second bushing 7 with the cylinder 5.
Viscous fluid damping materials 14 are filled in the damping cavity, a damping channel is arranged on the piston 6, when the viscous damper works, along with the reciprocating motion of the piston 6 relative to the cylinder barrel, the viscous fluid damping materials 14 flow from the high-pressure cavity to the low-pressure cavity through the damping channel on the piston 6, and energy is dissipated by overcoming factors such as friction and collision in the process that the viscous fluid damping materials 14 flow through the damping channel in a reciprocating mode.
When the piston 6 moves to and fro relative to the cylinder 5, and when the displacement-A is not less than U and not less than A, the damping force F is C | upsilon | when the displacement-A is not less than U and not more than AαSign (upsilon), wherein the damper only provides additional damping but not additional rigidity, the structural rigidity is flexible, so that relatively large displacement is obtained while earthquake reaction force is reduced, the hysteresis area of the damper is increased, a higher additional damping ratio is obtained, and the principle of reinforcing the structure by the additional damping achieves a higher performance target while the manufacturing cost is reduced by reducing the steel amount of the main structure and simultaneously the manufacturing cost is reduced by improving the additional damping ratio.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the right side relative to the cylinder barrel 5, the end face of the lug plate 12 abuts against the second spring seat 11 and pushes the second spring seat 11 to slide on the shaft head of the piston rod 2 to compress the spiral spring 10, the first spring seat 9 is abutted against the shaft shoulder on the piston rod 2 to keep relative rest with the piston rod 2 and provide reaction force for the spiral spring 10, and the displacement A is realized at the moment<U is more than or equal to U0, damping force F is C | upsilon-αSign (upsilon) + k (| U | -A), wherein C is the damping coefficient of the damper, α is the damping index of the damper, U is the displacement value of the damper, upsilon is the speed of the displacement point, and k is the speed of the coil spring 10 just beforeAnd (4) degree. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the left side relative to the cylinder barrel 5, the end face of the second threaded pressing pipe 8 props against the first spring seat 9 and pushes the first spring seat 9 to slide on the shaft head of the piston rod 2 to compress the spiral spring 10, the second spring seat 11 is propped against the nut 13 screwed on the screw rod of the piston rod 2 to keep relative rest with the piston rod 2 and provide a reaction force for the spiral spring 10, and at the moment, the displacement-U0 is not less than U>-a, damping force F ═ C | υ | non ¬ conducting lightαSign (upsilon) -k (| U | -A), wherein C is the damping coefficient of the damper, alpha is the damping index of the damper, U is the displacement value of the damper, upsilon is the speed of the displacement point, and k is the stiffness of the spiral spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
The first spring seat 9 and the second spring seat 11 are both sleeved on the shaft head of the piston rod 2 in an empty mode and can slide on the shaft head, compression of the spring group 10 in the stretching or compressing process of the damper is achieved, and additional rigidity in the stretching process of the damper and additional rigidity in the compressing process of the damper can be provided.
The damper has no additional rigidity applied in a hysteresis curve as shown in FIG. 4, the damper has additional rigidity applied in stages as shown in FIG. 5, and the damper has additional rigidity applied in stages as shown in FIG. 6.
Example 2
The variable additional rigidity viscous damper comprises a second lining 7, a first lining 4, a first threaded pressure pipe 3, a second threaded pressure pipe 8, an ear plate 12 and a piston rod 2, wherein the second lining 7 divides a cylinder barrel 5 into a damping cavity and an additional rigidity cavity, the first lining 4 is arranged at the end of the damping cavity, the first threaded pressure pipe 3 and the second threaded pressure pipe 8 are in threaded connection with the cylinder barrel 5 and are used for fixing the first lining 4 and the second lining 7 with the cylinder barrel 5, the ear plate 12 is arranged at the end part of the additional rigidity cavity and is fixed with the cylinder barrel 5 in a threaded connection mode, the piston rod 2 penetrates through a central inner hole of the first lining 4 and the second lining 7, one end of the piston rod 2 penetrates through the first lining 4 to extend out of the damping cavity to be fixed with a pin head 1, the other end of the piston rod 2 penetrates through the second lining 7 to be inserted into the additional rigidity cavity, a piston 6 is fixed on the piston rod 2, the damping cavity is divided into a left cavity and a right cavity by the piston 6, the part, which is designed into a stepped shaft structure, and the end of the piston rod 2 is provided with a shaft head and a large diameter smaller than the piston rod and keeps concentric with the piston rod A stud which is smaller than the shaft head and is concentric with the piston rod 2, a first spring seat 9 which is sleeved on the shaft head is arranged at the shaft shoulders of the shaft head and the piston rod 2, the stud adopts a screw connection mode to fix the nut 13 at the end part of the piston rod 2, the shoulder part formed by the end surface of the nut 13 and the shaft head is provided with a second spring seat 11 which is sleeved on the shaft head in a hollow way, a belleville spring 10 is arranged between the first spring seat 9 and the second spring seat 11, when the damper is at a displacement 0 point, the distance A is kept between the end surface of the first spring seat 9 close to the second threaded pressure pipe 8 and the end surface of the second threaded pressure pipe 8, the end face of the second spring seat 11 close to the lug plate 12 keeps the same distance A to the end face of the lug plate 12, a guide sleeve 4.1 and a piston rod seal 4.2 are arranged at the joint of the first bushing 4 and the second bushing 7 with the piston rod 2, and a bushing static seal 4.3 is arranged at the joint of the first bushing 4 and the second bushing 7 with the cylinder 5.
Viscous fluid damping materials 14 are filled in the damping cavity, a damping channel is arranged on the piston 6, when the viscous damper works, along with the reciprocating motion of the piston 6 relative to the cylinder barrel, the viscous fluid damping materials 14 flow from the high-pressure cavity to the low-pressure cavity through the damping channel on the piston 6, and energy is dissipated by overcoming factors such as friction and collision in the process that the viscous fluid damping materials 14 flow through the damping channel in a reciprocating mode.
When the piston 6 moves to and fro relative to the cylinder 5, and when the displacement-A is not less than U and not less than A, the damping force F is C | upsilon | when the displacement-A is not less than U and not more than AαSign (upsilon), where the damper provides only additional damping and not additional stiffness, making the structure stiffer and thus obtaining a relatively stiff while reducing seismic reaction forcesThe large displacement increases the hysteresis area of the damper to obtain higher additional damping ratio, and the principle of reinforcing the structure by the additional damping is utilized to realize the higher performance target while reducing the manufacturing cost by reducing the steel amount of the main body structure by improving the additional damping ratio.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the right side relative to the cylinder barrel 5, the end face of the lug plate 12 abuts against the second spring seat 11 and pushes the second spring seat 11 to slide on the shaft head of the piston rod 2 to compress the belleville spring 10, the first spring seat 9 is abutted against the shaft shoulder on the piston rod 2 to keep relative rest with the piston rod 2 and provide a reaction force for the belleville spring 10, and the displacement A is realized at the moment<U is more than or equal to U0, damping force F is C | upsilon-αSign (upsilon) + k (| U | -a), where C is the damping coefficient of the damper, α is the damping index of the damper, U is the displacement value of the damper, upsilon is the velocity of the displacement point, and k is the stiffness of the belleville spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the left side relative to the cylinder barrel 5, the end face of the second threaded pressing pipe 8 props against the first spring seat 9 and pushes the first spring seat 9 to slide on the shaft head of the piston rod 2 to compress the belleville spring 10, the second spring seat 11 props against the nut 13 screwed on the screw rod of the piston rod 2 to keep relative rest with the piston rod 2 and provide a reaction force for the belleville spring 10, and at the moment, the displacement-U0 is not less than U>-a, damping force F ═ C | υ | non ¬ conducting lightαSign (upsilon) -k (| U | -A), wherein C is the damping coefficient of the damper, alpha is the damping index of the damper, U is the displacement value of the damper, upsilon is the speed of the displacement point, and k is the stiffness of the belleville spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
The first spring seat 9 and the second spring seat 11 are both sleeved on the shaft head of the piston rod 2 in an empty mode and can slide on the shaft head, compression of the spring group 10 in the stretching or compressing process of the damper is achieved, and additional rigidity in the stretching process of the damper and additional rigidity in the compressing process of the damper can be provided.
The damper has no additional rigidity applied in a hysteresis curve as shown in FIG. 4, the damper has additional rigidity applied in stages as shown in FIG. 5, and the damper has additional rigidity applied in stages as shown in FIG. 6.
Example 3
The variable additional rigidity viscous damper comprises a second lining 7, a first lining 4, a first threaded pressure pipe 3, a second threaded pressure pipe 8, an ear plate 12 and a piston rod 2, wherein the second lining 7 divides a cylinder barrel 5 into a damping cavity and an additional rigidity cavity, the first lining 4 is arranged at the end of the damping cavity, the first threaded pressure pipe 3 and the second threaded pressure pipe 8 are in threaded connection with the cylinder barrel 5 and are used for fixing the first lining 4 and the second lining 7 with the cylinder barrel 5, the ear plate 12 is arranged at the end part of the additional rigidity cavity and is fixed with the cylinder barrel 5 in a threaded connection mode, the piston rod 2 penetrates through a central inner hole of the first lining 4 and the second lining 7, one end of the piston rod 2 penetrates through the first lining 4 to extend out of the damping cavity to be fixed with a pin head 1, the other end of the piston rod 2 penetrates through the second lining 7 to be inserted into the additional rigidity cavity, a piston 6 is fixed on the piston rod 2, the damping cavity is divided into a left cavity and a right cavity by the piston 6, the part, which is designed into a stepped shaft structure, and the end of the piston rod 2 is provided with a shaft head and a large diameter smaller than the piston rod and keeps concentric with the piston rod A stud which is smaller than the shaft head and is concentric with the piston rod 2, a first spring seat 9 which is sleeved on the shaft head is arranged at the shaft shoulders of the shaft head and the piston rod 2, the stud adopts a screw connection mode to fix the nut 13 at the end part of the piston rod 2, the shoulder part formed by the end surface of the nut 13 and the shaft head is provided with a second spring seat 11 which is sleeved on the shaft head in a hollow way, an annular spring 10 is arranged between the first spring seat 9 and the second spring seat 11, when the damper is at a displacement 0 point, the distance A is kept between the end surface of the first spring seat 9 close to the second threaded pressure pipe 8 and the end surface of the second threaded pressure pipe 8, the end face of the second spring seat 11 close to the lug plate 12 keeps the same distance A to the end face of the lug plate 12, a guide sleeve 4.1 and a piston rod seal 4.2 are arranged at the joint of the first bushing 4 and the second bushing 7 with the piston rod 2, and a bushing static seal 4.3 is arranged at the joint of the first bushing 4 and the second bushing 7 with the cylinder 5.
Viscous fluid damping materials 14 are filled in the damping cavity, a damping channel is arranged on the piston 6, when the viscous damper works, along with the reciprocating motion of the piston 6 relative to the cylinder barrel, the viscous fluid damping materials 14 flow from the high-pressure cavity to the low-pressure cavity through the damping channel on the piston 6, and energy is dissipated by overcoming factors such as friction and collision in the process that the viscous fluid damping materials 14 flow through the damping channel in a reciprocating mode.
When the piston 6 moves to and fro relative to the cylinder 5, and when the displacement-A is not less than U and not less than A, the damping force F is C | upsilon | when the displacement-A is not less than U and not more than AαSign (upsilon), wherein the damper only provides additional damping but not additional rigidity, the structural rigidity is flexible, so that relatively large displacement is obtained while earthquake reaction force is reduced, the hysteresis area of the damper is increased, a higher additional damping ratio is obtained, and the principle of reinforcing the structure by the additional damping achieves a higher performance target while the manufacturing cost is reduced by reducing the steel amount of the main structure and simultaneously the manufacturing cost is reduced by improving the additional damping ratio.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the right side relative to the cylinder barrel 5, the end face of the lug plate 12 abuts against the second spring seat 11 and pushes the second spring seat 11 to slide on the shaft head of the piston rod 2 to compress the annular spring 10, the first spring seat 9 is abutted against the shaft shoulder on the piston rod 2 to keep relative rest with the piston rod 2 and provide a reaction force for the annular spring 10, and the displacement A is realized at the moment<U is more than or equal to U0, damping force F is C | upsilon-αSign (upsilon) + k (| U | -a), where C is the damping coefficient of the damper, α is the damping index of the damper, U is the displacement value of the damper, upsilon is the velocity of the displacement point, and k is the stiffness of the ring spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
When the displacement amplitude exceeds the displacement amplitude in the process that the piston 6 moves towards the left side relative to the cylinder barrel 5A, the end face of the second threaded pressing pipe 8 abuts against the first spring seat 9 and pushes the first spring seat 9 to slide on the shaft head of the piston rod 2 to compress the annular spring 10, the second spring seat 11 abuts against the nut 13 screwed on the screw rod of the piston rod 2 to keep relative rest with the piston rod 2 and provide a reaction force for the annular spring 10, and at the moment, the displacement is equal to or greater than U0 and equal to U>-a, damping force F ═ C | υ | non ¬ conducting lightαSign (upsilon) -k (| U | -A), wherein C is the damping coefficient of the damper, alpha is the damping index of the damper, U is the displacement value of the damper, upsilon is the speed of the displacement point, and k is the stiffness of the annular spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
The first spring seat 9 and the second spring seat 11 are both sleeved on the shaft head of the piston rod 2 in an empty mode and can slide on the shaft head, compression of the spring group in the stretching or compressing process of the damper is achieved, and additional rigidity in the stretching process of the damper and additional rigidity in the compressing process of the damper can be provided.
The damper has no additional rigidity applied in a hysteresis curve as shown in FIG. 4, the damper has additional rigidity applied in stages as shown in FIG. 5, and the damper has additional rigidity applied in stages as shown in FIG. 6.
Example 4
The variable additional rigidity viscous damper comprises a second lining 7, a first lining 4, a first threaded pressure pipe 3, a second threaded pressure pipe 8, an ear plate 12 and a piston rod 2, wherein the second lining 7 divides a cylinder barrel 5 into a damping cavity and an additional rigidity cavity, the first lining 4 is arranged at the end of the damping cavity, the first threaded pressure pipe 3 and the second threaded pressure pipe 8 are in threaded connection with the cylinder barrel 5 and are used for fixing the first lining 4 and the second lining 7 with the cylinder barrel 5, the ear plate 12 is arranged at the end part of the additional rigidity cavity and is fixed with the cylinder barrel 5 in a threaded connection mode, the piston rod 2 penetrates through a central inner hole of the first lining 4 and the second lining 7, one end of the piston rod 2 penetrates through the first lining 4 to extend out of the damping cavity to be fixed with a pin head 1, the other end of the piston rod 2 penetrates through the second lining 7 to be inserted into the additional rigidity cavity, a piston 6 is fixed on the piston rod 2, the damping cavity is divided into a left cavity and a right cavity by the piston 6, the part, which is designed into a stepped shaft structure, and the end of the piston rod 2 is provided with a shaft head and a large diameter smaller than the piston rod and keeps concentric with the piston rod A stud which is smaller than the shaft head and is concentric with the piston rod 2, a first spring seat 9 which is sleeved on the shaft head in an empty way is arranged at the shaft shoulder of the shaft head and the piston rod 2, the stud fixes a nut 13 at the end part of the piston rod 2 in a threaded way, a second spring seat 11 which is sleeved on the shaft head in an empty way is arranged at the shoulder formed by the end surface of the nut 13 and the shaft head, an annular spring 10 is arranged between the first spring seat 9 and the second spring seat 11, the distance between the first spring seat 9 and the second spring seat 11 is changed by adjusting the nut 13 to enable the annular spring 10 to be pre-tightened and to keep the pre-tightening force Fn, when the damper is at a displacement 0 point, the end surface of the first spring seat 9, which is close to the second threaded pressure pipe 8, keeps a distance A from the end surface of the second spring seat 11, which is close to the ear plate 12, to the end surface of the ear plate 12, a same distance A is kept from the end surfaces of the first bush 4 and the second bush 7 to the piston rod 2, a guide bush 4.1 and a piston rod seal 4.2 are arranged at the connection part, and bushing static seals 4.3 are arranged at the joints of the first bushing 4 and the second bushing 7 and the cylinder 5.
Viscous fluid damping materials 14 are filled in the damping cavity, a damping channel is arranged on the piston 6, when the viscous damper works, along with the reciprocating motion of the piston 6 relative to the cylinder barrel, the viscous fluid damping materials 14 flow from the high-pressure cavity to the low-pressure cavity through the damping channel on the piston 6, and energy is dissipated by overcoming factors such as friction and collision in the process that the viscous fluid damping materials 14 flow through the damping channel in a reciprocating mode.
When the piston 6 moves to and fro relative to the cylinder 5, and when the displacement-A is not less than U and not less than A, the damping force F is C | upsilon | when the displacement-A is not less than U and not more than AαSign (upsilon), wherein the damper only provides additional damping but not additional rigidity, the structural rigidity is flexible, so that relatively large displacement is obtained while earthquake reaction force is reduced, the hysteresis area of the damper is increased, a higher additional damping ratio is obtained, and the principle of reinforcing the structure by the additional damping achieves a higher performance target while the manufacturing cost is reduced by reducing the steel amount of the main structure and simultaneously the manufacturing cost is reduced by improving the additional damping ratio.
The activityWhen the displacement amplitude exceeds A in the process that the plug 6 moves towards the right side relative to the cylinder barrel 5, the end face of the lug plate 12 abuts against the second spring seat 11 and pushes the second spring seat 11 to slide on the axial head of the piston rod 2 to compress the annular spring 10, the first spring seat 9 is abutted against the shaft shoulder on the piston rod 2 to keep relative rest with the piston rod 2 and provide reaction force for the annular spring 10, and the displacement A is realized at the moment<U is more than or equal to U0, damping force F is C | upsilon-αSign(υ)+k(|U|-A)+FnWherein C is the damping coefficient of the damper, α is the damping index of the damper, U is the displacement value of the damper, v is the velocity of the displacement point, and k is the stiffness of the annular spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the left side relative to the cylinder barrel 5, the end face of the second threaded pressing pipe 8 props against the first spring seat 9 and pushes the first spring seat 9 to slide on the shaft head of the piston rod 2 to compress the annular spring 10, the second spring seat 11 is propped against the nut 13 screwed on the screw rod of the piston rod 2 to keep relative rest with the piston rod 2 and provide reaction force for the annular spring 10, and at the moment, the displacement-U0 is not less than U>-a, damping force F ═ C | υ | non ¬ conducting lightαSign(υ)-k(|U|-A)-FnWherein C is the damping coefficient of the damper, α is the damping index of the damper, U is the displacement value of the damper, v is the velocity of the displacement point, and k is the stiffness of the annular spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
The first spring seat 9 and the second spring seat 11 are both sleeved on the shaft head of the piston rod 2 in an empty mode and can slide on the shaft head, compression of the spring group 10 in the stretching or compressing process of the damper is achieved, and additional rigidity in the stretching process of the damper and additional rigidity in the compressing process of the damper can be provided.
The hysteresis curve of the damper without applying additional stiffness is shown in fig. 4, the additional stiffness curve with spring belt pretension applied in stages is shown in fig. 7, and the hysteresis curve after applying the additional stiffness with spring belt pretension in stages is shown in fig. 8.
Example 5
The variable additional rigidity viscous damper comprises a second lining 7, a first lining 4, a first threaded pressure pipe 3, a second threaded pressure pipe 8, an ear plate 12 and a piston rod 2, wherein the second lining 7 divides a cylinder barrel 5 into a damping cavity and an additional rigidity cavity, the first lining 4 is arranged at the end of the damping cavity, the first threaded pressure pipe 3 and the second threaded pressure pipe 8 are in threaded connection with the cylinder barrel 5 and are used for fixing the first lining 4 and the second lining 7 with the cylinder barrel 5, the ear plate 12 is arranged at the end part of the additional rigidity cavity and is fixed with the cylinder barrel 5 in a threaded connection mode, the piston rod 2 penetrates through a central inner hole of the first lining 4 and the second lining 7, one end of the piston rod 2 penetrates through the first lining 4 to extend out of the damping cavity to be fixed with a pin head 1, the other end of the piston rod 2 penetrates through the second lining 7 to be inserted into the additional rigidity cavity, a piston 6 is fixed on the piston rod 2, the damping cavity is divided into a left cavity and a right cavity by the piston 6, the part, which is designed into a stepped shaft structure, and the end of the piston rod 2 is provided with a shaft head and a large diameter smaller than the piston rod and keeps concentric with the piston rod A stud which is smaller than the shaft head and concentric with the piston rod 2 is kept, a first spring seat 9 which is sleeved on the shaft head in an empty mode is arranged at the shaft shoulder position of the shaft head and the piston rod 2, a nut 13 is fixed at the end part of the piston rod 2 by the stud in a threaded mode, a second spring seat 11 which is sleeved on the shaft head in an empty mode is arranged at the shoulder part formed by the end surface of the nut 13 and the shaft head, an annular spring group 10 is arranged between the first spring seat 9 and the second spring seat 11, the annular spring group 10 is composed of an annular spring 10.1 which is arranged at the outer layer and an annular spring 10.2 which is arranged at the inner layer in a parallel relation, when the damper is at a displacement 0 point, a distance A is kept between the end surface of the first spring seat 9, which is close to the second threaded pressure pipe 8, and the end surface of the second threaded pressure pipe 8, a distance A is kept between the end surface of the second spring seat 11, which is close to the ear plate 12, and the end surface of the ear plate 12, and the same distance A is kept between the end surface of the annular spring 10.2 and the second spring seat 11, and the end surface of the first spring seat 9, and the first spring seat 9 are kept in a step Keeping distance A2, a guide sleeve 4.1 and a piston rod seal 4.2 are arranged at the joint of the first bushing 4 and the second bushing 7 with the piston rod 2, and a bushing static seal 4.3 is arranged at the joint of the first bushing 4 and the second bushing 7 with the cylinder 5.
Viscous fluid damping materials 14 are filled in the damping cavity, a damping channel is arranged on the piston 6, when the viscous damper works, along with the reciprocating motion of the piston 6 relative to the cylinder barrel, the viscous fluid damping materials 14 flow from the high-pressure cavity to the low-pressure cavity through the damping channel on the piston 6, and energy is dissipated by overcoming factors such as friction and collision in the process that the viscous fluid damping materials 14 flow through the damping channel in a reciprocating mode.
When the piston 6 moves to and fro relative to the cylinder 5, and when the displacement-A is not less than U and not less than A, the damping force F is C | upsilon | when the displacement-A is not less than U and not more than AαSign (upsilon), wherein the damper only provides additional damping but not additional rigidity, the structural rigidity is flexible, so that relatively large displacement is obtained while earthquake reaction force is reduced, the hysteresis area of the damper is increased, a higher additional damping ratio is obtained, and the principle of reinforcing the structure by the additional damping achieves a higher performance target while the manufacturing cost is reduced by reducing the steel amount of the main structure and simultaneously the manufacturing cost is reduced by improving the additional damping ratio.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the right side relative to the cylinder barrel 5, the end face of the lug plate 12 abuts against the second spring seat 11 and pushes the second spring seat 11 to slide on the shaft head of the piston rod 2 to compress the annular spring group 10, the first spring seat 9 is abutted against the shaft shoulder on the piston rod 2 to keep relative rest with the piston rod 2 and provide a counterforce for the annular spring group 10, and when the displacement A exceeds A, the first spring seat 9 abuts against the shaft shoulder on the piston rod 2 to keep relative rest with the piston rod 2 and provides a counterforce for the annular spring group 10<When U is more than or equal to A1, damping force F is C | upsilon-αSign(υ)+k1(| U | -A), when the displacement is A1<When U is more than or equal to U0, damping force F is C | upsilon-αSign(υ)+k1(|U|-A)+k2(|U|-A-A2) Wherein C is the damping coefficient of the damper, alpha is the damping index of the damper, U is the displacement value of the damper, upsilon is the speed of the displacement point, k1 is the rigidity of the annular spring 10.1, and k2 is the rigidity of the annular spring 10.2. In the process, the damper provides additional damping and provides additional rigidity applied in multiple stages for the main body structure, so that the main body structure can be effectively controlled in the middle earthquake, the major earthquake and the rare earthquakeThe displacement angle between layers under action protects the main structure from damage in terms of both strength and rigidity improvement.
When the displacement amplitude exceeds A in the process that the piston 6 moves towards the left side relative to the cylinder barrel 5, the end face of the second threaded pressing pipe 8 props against the first spring seat 9 and pushes the first spring seat 9 to slide on the shaft head of the piston rod 2 to compress the annular spring 10, the second spring seat 11 is propped against the nut 13 screwed on the screw rod of the piston rod 2 to keep relative rest with the piston rod 2 and provide a reaction force for the annular spring 10, and when the displacement-A1 is not more than U>Damping force F ═ C | υ tintaαS i(gυ)n-k1(| U | -A), when the displacement-U0 is not more than U>Damping force F ═ C | υ | when a1 is zeroαS i(gυ)n-k1(|U|-A)-k2(|U|-A-A2) Wherein C is the damping coefficient of the damper, α is the damping index of the damper, U is the displacement value of the damper, v is the velocity of the displacement point, k1 is the stiffness of the annular spring 10.1, and k2 is the stiffness of the annular spring 10.2. In the process, the damper provides additional damping and provides additional rigidity applied in multiple stages for the main body structure, so that the interlayer displacement angle of the main body structure under the action of medium earthquakes, large earthquakes and rare earthquakes can be effectively controlled, and the main body structure is protected from being damaged in the aspects of strength and rigidity improvement.
The first spring seat 9 and the second spring seat 11 are both sleeved on the shaft head of the piston rod 2 in an empty mode and can slide on the shaft head, compression of the spring group 10 in the stretching or compressing process of the damper is achieved, and additional rigidity in the stretching process of the damper and additional rigidity in the compressing process of the damper can be provided.
The damper has no additional rigidity applied in the hysteresis curve as shown in FIG. 4, multiple stages of additional rigidity applied in the hysteresis curve as shown in FIG. 10, and multiple stages of additional rigidity applied in the hysteresis curve as shown in FIG. 11.
It is to be understood that the above-described embodiments of the present invention are merely illustrative of or explaining the principles of the invention and are not to be construed as limiting the invention. Therefore, any modification, equivalent replacement, improvement and the like made without departing from the spirit and scope of the present invention should be included in the protection scope of the present invention. Further, it is intended that the appended claims cover all such variations and modifications as fall within the scope and boundaries of the appended claims or the equivalents of such scope and boundaries.
Claims (9)
1. A variable additional rigidity viscous damper comprises a second lining (7) dividing a cylinder barrel (5) into a damping cavity and an additional rigidity cavity, a first lining (4) arranged at the end of the damping cavity, a first thread pressure pipe (3) and a second thread pressure pipe (8) which are screwed with the cylinder barrel (5) and used for fixing the first lining (4) and the second lining (7) with the cylinder barrel (5), an ear plate (12) which is arranged at the end part of the additional rigidity cavity and fixed with the cylinder barrel (5) in a screwing mode, a piston rod (2) which penetrates through central inner holes of the first lining (4) and the second lining (7), a pin head (1) which is arranged outside the damper cylinder barrel (5) and fixed with the end part of the piston rod (2), a piston (6) which is fixed on the piston rod (2) and arranged in the damping cavity to divide the damping cavity into a left cavity and a right cavity, and viscous fluid damping materials (14) which are filled in the damping cavity, the method is characterized in that: the part of the piston rod (2) inserted into the additional stiffness cavity is designed into a stepped shaft structure, a shaft head with a diameter smaller than that of the piston rod and concentric with the piston rod and a stud with a large diameter smaller than that of the shaft head and concentric with the piston rod are arranged, a first spring seat (9) which is sleeved on the shaft head in a hollow mode is arranged at the shaft shoulder of the shaft head and the piston rod (2), the stud and a nut (13) are fixed in a threaded mode, a second spring seat (11) which is sleeved on the shaft head in a hollow mode is arranged at the shoulder formed by the end portion of the nut (13) and the shaft head, and a spring set (10) is arranged between the first spring seat (9) and the second spring seat (11).
2. The viscous damper with variable additional rigidity according to claim 1, characterized in that: when the piston (6) is at the displacement 0 point, the distance from the end surface of the piston close to the first lining (4) to the end surface of the first lining (4) is the limit displacement U of the damper0The distance between the end surface close to the second bush (7) and the end surface of the second bush (7) is the limit displacement U of the damper0The distance A from the end face of the first spring seat (9) to the end face of the second threaded pressure pipe (8) needs to satisfy 0-A>U0Second spring seat(11) The distance A from the end face to the end face of the ear plate (12) needs to satisfy 0-A>U0And the working stroke plus the distance A of the spring group is more than or equal to the limit displacement U0。
3. The viscous damper with variable additional rigidity according to claim 1, characterized in that: the spring group (10) is a single spring, a plurality of parallel springs, a plurality of series springs and a series-parallel combined spring.
4. The viscous damper with variable additional rigidity according to claim 1 or 3, characterized in that: the springs adopted by the spring group (10) are helical springs, belleville springs, annular springs and special-shaped springs.
5. The viscous damper with variable additional rigidity according to claim 1, characterized in that: the first spring seat (9) and the second spring seat (11) are sleeved on the shaft head of the piston rod (2) in an empty mode.
6. The viscous damper with variable additional rigidity according to claim 1, characterized in that: and a damping channel is arranged on the piston (6).
7. The viscous damper with variable additional rigidity according to claim 1, characterized in that: the joint of the first bushing (4) and the piston rod (2) is provided with a guide sleeve (4.1) and a piston rod seal (4.2).
8. The viscous damper with variable additional rigidity according to claim 1, characterized in that: the joint of the second bush (7) and the piston rod (2) is provided with a guide sleeve (4.1) and a piston rod seal (4.2).
9. The viscous damper with variable additional rigidity according to claim 1, characterized in that: and bushing static seals (4.3) are arranged at the joints of the first bushing (4), the second bushing (7) and the cylinder barrel (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120682104.0U CN214835226U (en) | 2021-04-02 | 2021-04-02 | Variable additional rigidity viscous damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120682104.0U CN214835226U (en) | 2021-04-02 | 2021-04-02 | Variable additional rigidity viscous damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214835226U true CN214835226U (en) | 2021-11-23 |
Family
ID=78761714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202120682104.0U Active CN214835226U (en) | 2021-04-02 | 2021-04-02 | Variable additional rigidity viscous damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN214835226U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117905188A (en) * | 2024-03-19 | 2024-04-19 | 四川中震智控科技有限公司 | Viscous damper with adjustable rigidity |
-
2021
- 2021-04-02 CN CN202120682104.0U patent/CN214835226U/en active Active
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN117905188A (en) * | 2024-03-19 | 2024-04-19 | 四川中震智控科技有限公司 | Viscous damper with adjustable rigidity |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN106090402B (en) | A kind of driving device and valve actuator based on gas-liquid cluster spring | |
| CN201843226U (en) | Variable-rigidity friction type energy-consumption damping device | |
| CN206972817U (en) | A kind of spring air damper | |
| US20240093753A1 (en) | Damper with hydraulic compression stop | |
| CN113202200B (en) | Self-resetting viscous damper based on combined spring | |
| CN214835226U (en) | Variable additional rigidity viscous damper | |
| CN117905188B (en) | Viscous damper with adjustable rigidity | |
| US20040060787A1 (en) | Cylinder apparatus | |
| CN113187842A (en) | Multi-stage damping force viscous damper | |
| CN113202896A (en) | Composite vibration-damping and impact-resisting device and vibration-damping method for metal rubber and elastic daub | |
| CN111441493B (en) | Viscous-viscoelastic composite damper | |
| CN113152973A (en) | Variable additional rigidity viscous damper | |
| CN106369095B (en) | A kind of disk spring damper that can adjust early stage rigidity | |
| CN105587816B (en) | A kind of large-tonnage elasticity-damping composite shock-absorbing device | |
| CN112609855B (en) | One-way self-resetting adjustable friction energy dissipation damper and use method thereof | |
| CN215977833U (en) | Self-resetting viscous damper based on combined spring | |
| CN110957689B (en) | Power cable prevents waving device | |
| CN210290574U (en) | Double-cylinder double-air-chamber hydro-pneumatic spring | |
| CN211574129U (en) | Internal pressure self-adjusting viscous damper | |
| CN107477133A (en) | A kind of single-piston rod hydraulic damper | |
| CN109667876B (en) | Oil pressure shock absorber piston and oil pressure shock absorber | |
| CN111120566A (en) | High-energy pipeline whipping prevention device | |
| CN220118556U (en) | Hydraulic high-safety transverse shock absorber | |
| CN216279141U (en) | Multi-stage damping force viscous damper | |
| CN112253665A (en) | Two-stage vibration isolation buffer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant |