CN113152973A - Variable additional rigidity viscous damper - Google Patents

Variable additional rigidity viscous damper Download PDF

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Publication number
CN113152973A
CN113152973A CN202110362017.1A CN202110362017A CN113152973A CN 113152973 A CN113152973 A CN 113152973A CN 202110362017 A CN202110362017 A CN 202110362017A CN 113152973 A CN113152973 A CN 113152973A
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China
Prior art keywords
damper
spring
damping
piston rod
cavity
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CN202110362017.1A
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Inventor
杨勇
唐均
温文露
马振霄
管庆松
魏德超
施立新
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Zhenan Technology Co Ltd
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Zhenan Technology Co Ltd
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Priority to CN202110362017.1A priority Critical patent/CN113152973A/en
Publication of CN113152973A publication Critical patent/CN113152973A/en
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    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04H—BUILDINGS OR LIKE STRUCTURES FOR PARTICULAR PURPOSES; SWIMMING OR SPLASH BATHS OR POOLS; MASTS; FENCING; TENTS OR CANOPIES, IN GENERAL
    • E04H9/00—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate
    • E04H9/02—Buildings, groups of buildings or shelters adapted to withstand or provide protection against abnormal external influences, e.g. war-like action, earthquake or extreme climate withstanding earthquake or sinking of ground
    • E04H9/021—Bearing, supporting or connecting constructions specially adapted for such buildings
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04B—GENERAL BUILDING CONSTRUCTIONS; WALLS, e.g. PARTITIONS; ROOFS; FLOORS; CEILINGS; INSULATION OR OTHER PROTECTION OF BUILDINGS
    • E04B1/00—Constructions in general; Structures which are not restricted either to walls, e.g. partitions, or floors or ceilings or roofs
    • E04B1/62—Insulation or other protection; Elements or use of specified material therefor
    • E04B1/92—Protection against other undesired influences or dangers
    • E04B1/98—Protection against other undesired influences or dangers against vibrations or shocks; against mechanical destruction, e.g. by air-raids

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  • Engineering & Computer Science (AREA)
  • Architecture (AREA)
  • Environmental & Geological Engineering (AREA)
  • Business, Economics & Management (AREA)
  • Emergency Management (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Vibration Prevention Devices (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)

Abstract

The invention relates to the technical field of dampers, in particular to a variable additional rigidity viscous damper; 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

Variable additional rigidity viscous damper
Technical Field
The invention relates to the technical field of dampers, in particular to a variable 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 a strong earthquake, 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 earthquake 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 reducing the steel amount of the main body structure, reducing the manufacturing cost and obtaining higher performance while improving the additional damping ratio; the main structure is additionally provided with an additional rigidity while providing additional damping 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 invent 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 structural layers of the main body to reduce structural damage.
Disclosure of Invention
Aiming at the defects of the prior art, the invention provides a variable additional stiffness viscous damper, which does not provide additional stiffness under wind vibration and small earthquake by adopting a staged working mode through a spring group arranged in an additional stiffness cavity so as to ensure that the structural stiffness is softer, thereby obtaining relatively larger displacement while reducing earthquake reaction force, increasing the hysteresis area of the damper to obtain higher additional damping ratio, and realizing the purposes of reducing the steel amount of a main structure, reducing the manufacturing cost and obtaining higher performance 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 the medium earthquake, the large earthquake and the rare earthquake, the interlayer displacement angle of the main structure under the effects of the medium earthquake, the large earthquake and the rare earthquake 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 problems, the invention 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 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 a piston rod, a piston fixed on the piston rod and arranged in the damping cavity and dividing the damping cavity into a left cavity and a right cavity, viscous fluid damping material filled in the damping cavity, a 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 keeping concentricity with the piston rod and a stud with a diameter smaller than the shaft head and keeping concentricity 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 medium earthquake, the large earthquake and the rare earthquake is effectively controlled, the effect that the additional stiffness is not provided under the wind vibration and the small earthquake to ensure that the structure has softer stiffness is achieved, so that the earthquake reaction force is reduced, meanwhile, a relatively large displacement is obtained, the hysteresis area of the damper is increased to obtain a higher additional damping ratio, and the principle of reinforcing the structure by the additional damping is utilized to achieve the purpose of reducing the steel amount of the main structure and reducing the manufacturing cost and simultaneously obtaining a higher performance target by improving the additional damping ratio; the main structure is additionally provided with additional rigidity while providing additional damping 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 must satisfy 0-A > U0, the distance A from the end face of the second spring seat to the end face of the lug plate must 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 a hollow 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 invention has at least one of the following beneficial effects: the invention provides a variable additional stiffness viscous damper, which does not provide additional stiffness under wind vibration and small earthquake by adopting a staged working mode through a spring group arranged in an additional stiffness cavity so as to ensure that the structural stiffness is softer, thereby obtaining relatively larger displacement while reducing earthquake reaction force, increasing the hysteresis area of the damper to obtain higher additional damping ratio, and realizing the purpose of reducing the steel amount of a main structure and reducing the manufacturing cost and obtaining higher performance by improving the additional damping ratio by utilizing the principle of reinforcing the structure by utilizing 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.
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 diagram illustrating the operation of the variable additional stiffness viscous damper according to the present invention in a stretched 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 plot of hysteresis after additional stiffness applied in stages of the present invention.
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 the additional stiffness of the present invention is applied in stages with the spring pre-loaded.
Fig. 9 is a structural schematic diagram of a multi-stage additional rate spring set of the present invention.
FIG. 10 is a graph of additional stiffness applied in multiple stages of the present invention.
FIG. 11 is a plot of hysteresis after the multi-stage application of additional stiffness of the present invention.
In the figure: 1-pin head, 2-piston rod, 3-first thread pressing 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 pressing pipe, 9-first spring seat, 10-spring group, 10.1-first spring, 10.2-second spring, 11-second spring seat, 12-ear 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 embodiments. 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
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 threaded pressure pipe 3 and a second threaded pressure pipe 8 which 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, an ear plate 12 arranged at the end of the additional rigidity cavity and fixed with the cylinder barrel 5 in a threaded connection mode, a piston rod 2 penetrating through central inner holes of the first lining 4 and the second lining 7, one end of the piston rod 2 extending out of the damping cavity through the first lining 4 to be fixed with a pin head 1, the other end of the piston rod penetrating 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, and the part of the piston rod 2 inserted into the additional rigidity cavity is designed into a stepped shaft structure, the end of the piston rod 2 is provided with a section of shaft head with the diameter smaller than the piston rod and concentric with the piston rod and a section of stud with the major diameter smaller than the shaft head and 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 of the piston rod 2 in a screwing 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, a spiral spring 10 is arranged between the first spring seat 9 and the second spring seat 11, when the damper is at the 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 distance A is kept between the end surface of the second spring seat 11 close to the ear plate 12 and the end surface of the ear plate 12 in the same way, and the joint of the first bush 4 and the second bush 7 and the piston rod 2 is provided with a guide sleeve 4.1 and a piston rod seal 4.2, 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 ratio is utilized to achieve the aim of obtaining higher performance while reducing the manufacturing cost by reducing the steel amount of the main body structure.
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 a counterforce 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), 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 coil spring 10. In the process, the damper provides additional damping and provides additional rigidity applied in a staged manner 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 piston 6 is opposite to the cylinder 5 in directionWhen the displacement amplitude exceeds A in the left-side movement process, 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 spiral spring 10, the second spring seat 11 is abutted 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 is equal to or less than U0>-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
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 threaded pressure pipe 3 and a second threaded pressure pipe 8 which 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, an ear plate 12 arranged at the end of the additional rigidity cavity and fixed with the cylinder barrel 5 in a threaded connection mode, a piston rod 2 penetrating through central inner holes of the first lining 4 and the second lining 7, one end of the piston rod 2 extending out of the damping cavity through the first lining 4 to be fixed with a pin head 1, the other end of the piston rod penetrating 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, and the part of the piston rod 2 inserted into the additional rigidity cavity is designed into a stepped shaft structure, the end of the piston rod 2 is provided with a section of shaft head with the diameter smaller than the piston rod and concentric with the piston rod and a section of stud with the major diameter smaller than the shaft head and concentric with the piston rod 2, a first spring seat 9 which is sleeved on the shaft head in a hollow 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 of the piston rod 2 in a screw connection way, a second spring seat 11 which is sleeved on the shaft head in a hollow way is arranged at the shoulder formed by the end surface of the nut 13 and the shaft head, a butterfly spring 10 is arranged between the first spring seat 9 and the second spring seat 11, when the damper is at the 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 distance A is kept between the end surface of the second spring seat 11 close to the ear plate 12 and the end surface of the ear plate 12 in the same way, and the connection part of the first bush 4 and the second bush 7 and the piston rod 2 is provided with a guide sleeve 4.1 and a piston rod seal 4.2, 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 ratio is utilized to achieve the aim of obtaining higher performance while reducing the manufacturing cost by reducing the steel amount of the main body structure.
The piston 6 is in the right movement process relative to the cylinder 5After the displacement amplitude exceeds A, 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, the butterfly spring 10 is compressed, the first spring seat 9 is abutted against the shaft shoulder on the piston rod 2 and is kept stationary relative to the piston rod 2 and provides a reaction force for the butterfly spring 10, and at the moment, the displacement A is displaced<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 a staged manner 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
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 threaded pressure pipe 3 and a second threaded pressure pipe 8 which 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, an ear plate 12 arranged at the end of the additional rigidity cavity and fixed with the cylinder barrel 5 in a threaded connection mode, a piston rod 2 penetrating through central inner holes of the first lining 4 and the second lining 7, one end of the piston rod 2 extending out of the damping cavity through the first lining 4 to be fixed with a pin head 1, the other end of the piston rod penetrating 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, and the part of the piston rod 2 inserted into the additional rigidity cavity is designed into a stepped shaft structure, the end of the piston rod 2 is provided with a section of shaft head with the diameter smaller than the piston rod and concentric with the piston rod and a section of stud with the major diameter smaller than the shaft head and 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 of the piston rod 2 in a screwing 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, 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 distance A is kept between the end surface of the second spring seat 11 close to the ear plate 12 and the end surface of the ear plate 12, and the connecting part of the first bush 4 and the second bush 7 and the piston rod 2 is provided with a guide sleeve 4.1 and a piston rod seal 4.2, 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 ratio is utilized to achieve the aim of obtaining higher performance while reducing the manufacturing cost by reducing the steel amount of the main body structure.
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 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 a staged manner 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 a reaction for the annular spring 10Force, at this time displacement-U0 ≤ 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
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 threaded pressure pipe 3 and a second threaded pressure pipe 8 which 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, an ear plate 12 arranged at the end of the additional rigidity cavity and fixed with the cylinder barrel 5 in a threaded connection mode, a piston rod 2 penetrating through central inner holes of the first lining 4 and the second lining 7, one end of the piston rod 2 extending out of the damping cavity through the first lining 4 to be fixed with a pin head 1, the other end of the piston rod penetrating 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, and the part of the piston rod 2 inserted into the additional rigidity cavity is designed into a stepped shaft structure, the end of the piston rod 2 is provided with a section of shaft head with a diameter smaller than the piston rod and concentric with the piston rod and a section of stud with a large diameter smaller than the shaft head and concentric with the piston rod 2, a first spring seat 9 which is sleeved on the shaft head is arranged at the shaft shoulder of the shaft head and the piston rod 2 in a hollow way, the stud fixes a nut 13 on the end of the piston rod 2 in a screw connection way, a second spring seat 11 which is sleeved on the shaft head in a hollow way is arranged on 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 annular spring 10 is pre-tightened and keeps pre-tightening force Fn by changing the distance between the first spring seat 9 and the second spring seat 11 through adjusting the nut 13, and the distance from the end surface of the first spring seat 9 close to the second threaded pressure pipe 8 to the end surface of the second threaded pressure pipe 8 keeps A when the damper is at the displacement 0 point, 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 ratio is utilized to achieve the aim of obtaining higher performance while reducing the manufacturing cost by reducing the steel amount of the main body structure.
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, and the first spring seat 9 is abutted against by the shaft shoulder on the piston rod 2Remains stationary relative to the piston rod 2 and provides a reaction force for the annular spring 10, at which displacement a occurs<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, υ 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 a staged manner 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 damper has no additional stiffness applied, and is shown in a hysteresis curve in fig. 4, a spring pre-tightening additional stiffness curve in stages is shown in fig. 7, and the damper applies the spring pre-tightening additional stiffness curve in stages is shown in a hysteresis curve in fig. 8.
Example 5
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 threaded pressure pipe 3 and a second threaded pressure pipe 8 which 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, an ear plate 12 arranged at the end of the additional rigidity cavity and fixed with the cylinder barrel 5 in a threaded connection mode, a piston rod 2 penetrating through central inner holes of the first lining 4 and the second lining 7, one end of the piston rod 2 extending out of the damping cavity through the first lining 4 to be fixed with a pin head 1, the other end of the piston rod penetrating 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, and the part of the piston rod 2 inserted into the additional rigidity cavity is designed into a stepped shaft structure, the end of the piston rod 2 is provided with a section of shaft head with the diameter smaller than the piston rod and concentric with the piston rod and a section of stud with the major diameter smaller than the shaft head and 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 of the piston rod 2 in a screwing 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 group 10 is arranged between the first spring seat 9 and the second spring seat 11, the annular spring group 10 consists 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, and when the damper is at the displacement 0 point, the 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, the same distance A is kept from the end face of the second spring seat 11 close to the lug plate 12 to the end face of the lug plate 12, the annular spring 10.2 is fixed on the second spring seat 11 and enables the end face of the annular spring close to the first spring seat 9 to keep a distance A2 from the step face of the first spring seat 9, 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 ratio is utilized to achieve the aim of obtaining higher performance while reducing the manufacturing cost by reducing the steel amount of the main body structure.
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 piston 6 moves towards the right side relative to the cylinder barrel 5<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 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 improving the strength and the rigidity.
The piston 6 moves leftwards relative to the cylinder 5When the displacement amplitude exceeds A, 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 axial 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 when the displacement is equal to or larger than U, the displacement is equal to-A1>Damping force F ═ C | υ tintaαSign(υ)-k1(| U | -A), when the displacement-U0 is not more than U>Damping force F ═ C | υ | when a1 is zeroαSign(υ)-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 (6)

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).
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>U0The distance A from the end face of the second spring seat (11) to the end face of the lug 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 2, characterized in that: the theoretical damping force calculation formula of the damper is as follows: when-U0≤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<U≥U0When F ═ 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, FnFor pre-tightening the spring set, the pre-tightening of the spring set (10) is Fn>0, if the spring set (10) is not pre-tensioned, Fn＝0。
4. The viscous damper with variable additional rigidity according to claim 1, characterized in that: the spring group (10) can be a single spring, a plurality of parallel springs, a plurality of series springs and a series-parallel combined spring.
5. The viscous damper with variable additional rigidity according to claim 1 or 4, characterized in that: the spring adopted by the spring group (10) can be a spiral spring, a belleville spring, a ring spring and a special-shaped spring.
6. 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.
CN202110362017.1A 2021-04-02 2021-04-02 Variable additional rigidity viscous damper Pending CN113152973A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202110362017.1A CN113152973A (en) 2021-04-02 2021-04-02 Variable additional rigidity viscous damper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202110362017.1A CN113152973A (en) 2021-04-02 2021-04-02 Variable additional rigidity viscous damper

Publications (1)

Publication Number Publication Date
CN113152973A true CN113152973A (en) 2021-07-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202110362017.1A Pending CN113152973A (en) 2021-04-02 2021-04-02 Variable additional rigidity viscous damper

Country Status (1)

Country Link
CN (1) CN113152973A (en)

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