CN117150953A - Method and system for predicting damping force of double-order viscous damper - Google Patents

Method and system for predicting damping force of double-order viscous damper Download PDF

Info

Publication number
CN117150953A
CN117150953A CN202311057239.8A CN202311057239A CN117150953A CN 117150953 A CN117150953 A CN 117150953A CN 202311057239 A CN202311057239 A CN 202311057239A CN 117150953 A CN117150953 A CN 117150953A
Authority
CN
China
Prior art keywords
piston
damping force
stage
damping
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN202311057239.8A
Other languages
Chinese (zh)
Other versions
CN117150953B (en
Inventor
解琳琳
杨参天
李爱群
王昊祥
孙航
何洋
刘冰燕
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Beijing University of Civil Engineering and Architecture
Original Assignee
Beijing University of Civil Engineering and Architecture
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Beijing University of Civil Engineering and Architecture filed Critical Beijing University of Civil Engineering and Architecture
Priority to CN202311057239.8A priority Critical patent/CN117150953B/en
Publication of CN117150953A publication Critical patent/CN117150953A/en
Application granted granted Critical
Publication of CN117150953B publication Critical patent/CN117150953B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/28—Design optimisation, verification or simulation using fluid dynamics, e.g. using Navier-Stokes equations or computational fluid dynamics [CFD]
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
    • G06F2111/10—Numerical modelling
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2113/00—Details relating to the application field
    • G06F2113/08—Fluids
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Theoretical Computer Science (AREA)
  • Mathematical Physics (AREA)
  • Fluid Mechanics (AREA)
  • Mathematical Analysis (AREA)
  • Mathematical Optimization (AREA)
  • Computing Systems (AREA)
  • Pure & Applied Mathematics (AREA)
  • Computer Hardware Design (AREA)
  • Evolutionary Computation (AREA)
  • Geometry (AREA)
  • General Engineering & Computer Science (AREA)
  • Algebra (AREA)
  • Fluid-Damping Devices (AREA)

Abstract

The invention provides a method and a system for predicting damping force of a double-order viscous damper, wherein the method comprises the following steps: only calculating the pressure difference between two ends of the main piston in the first stage; calculating a damping force of a hole of the main piston according to the pressure difference between two ends of the main piston at the first stage, and taking the damping force as a damping force of the viscous damper at the first stage; respectively calculating the differential pressure of two ends of the primary piston and the secondary piston in the transition section and the second stage; and calculating a primary piston damping force according to the differential pressure between two ends of the primary piston, calculating a secondary piston damping force according to the differential pressure between two ends of the secondary piston, and taking the sum of the primary piston pore damping force and the secondary piston damping force as the viscous damper damping force of the transition section or the second stage. The embodiment of the invention can effectively predict the damping force of the dual-order viscous damper, is more accurate compared with the damping force calculated by directly utilizing the calculation method of the superposition of the damping force of the traditional viscous damper, and can effectively develop the structural seismic response analysis of the dual-order viscous damper.

Description

Method and system for predicting damping force of double-order viscous damper
Technical Field
The invention relates to the technical field of structural vibration reduction control, in particular to a method and a system for predicting damping force of a double-order viscous damper.
Background
Earthquake is a natural disaster unavoidable to human society, and casualties and economic losses caused by earthquake are mostly caused by building collapse. Therefore, the construction field provides a passive control technology, and the passive control technology mainly adopts two methods of energy dissipation and vibration isolation, and the energy dissipation and vibration isolation method is one of the main means of modern society vibration-resistant design because of simplicity and reliability. The energy dissipation and shock absorption method controls the dynamic response of the building structure under the action of earthquake by introducing some mechanical devices capable of dissipating earthquake energy, thereby achieving the effect of protecting the main structure.
The viscous damper is a damper with wide application. By the reciprocating motion of the piston in the damper, the high-viscosity fluid passes through the small hole on the piston or the gap between the piston and the cylinder barrel at high speed under the action of pressure difference to generate damping. Meanwhile, the viscous fluid damper is used as a hydraulic device, has no additional rigidity in a low-frequency range, and is a speed-dependent damper. The existence of the passive control of the structure successfully reduces the displacement of the top and lower floors by numerical analysis of the seismic response of the reinforced concrete frame with viscous dampers.
However, the conventional single-order viscous damper cannot meet higher requirements, and the requirements of different working states are met by changing the structure of the viscous damper at present, so that the structure and the working mechanism of the double-order viscous damper are available on the market.
The double-order viscous damper mainly comprises a main cylinder barrel, an auxiliary cylinder barrel, a piston rod, a main piston fixedly sleeved on the piston rod, a secondary cylinder barrel arranged between the main cylinder barrel and the auxiliary cylinder barrel, a secondary piston fixedly sleeved on the piston rod and the like, wherein damping holes are formed in the main piston and the secondary piston. The motion of the piston rod can drive the main piston and the secondary piston to jointly move, and the section of the inner wall of the secondary cylinder barrel is changed, so that the gaps between the secondary piston and the inner wall of the secondary cylinder barrel can be changed in the motion process, and the requirements of different working states are met.
However, the existing calculation method of the single-order viscous damper cannot be applied to the double-order viscous damper, so that the structural seismic response analysis is difficult to develop.
Disclosure of Invention
In order to solve the above problems, an embodiment of the present invention provides a method for predicting a damping force of a dual-order viscous damper, where when a secondary piston of the dual-order viscous damper is in a first stage, the damping force includes a primary piston pore flow damping force; when the secondary piston of the damper is positioned in the transition section, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, wherein the secondary piston gap flow damping force is related to the position and the movement speed of the secondary piston; after the secondary piston of the damper completely enters the second stage, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, and after the secondary piston completely enters the second stage, the secondary piston gap flow damping force is only related to the movement speed of the secondary piston;
The method comprises the following steps: in the first stage, acquiring a main piston pore flow rate, and calculating a pressure difference between two ends of the main piston in the first stage according to the main piston pore flow rate; calculating a damping force of a hole of the main piston according to the pressure difference between two ends of the main piston at the first stage, and taking the damping force as a damping force of the viscous damper at the first stage; or in the transition section and the second stage, obtaining a primary piston pore flow rate, a secondary piston pore flow rate and a gap flow rate, calculating a differential pressure at two ends of a primary piston according to the primary piston pore flow rate, and calculating a differential pressure at two ends of a secondary piston according to the sum of the secondary piston pore flow rate and the gap flow rate; and calculating a primary piston damping force according to the differential pressure between two ends of the primary piston, calculating a secondary piston damping force according to the differential pressure between two ends of the secondary piston, and taking the sum of the primary piston pore damping force and the secondary piston damping force as the viscous damper damping force of the transition section or the second stage.
Optionally, the primary piston aperture flow rate of the first stage is as follows:
wherein m is the flow index; k is the consistency coefficient; l is the width of the piston, namely the length of the circular tube; s is that the piston is provided with s groups of round holes with different apertures; r is R i Is the radius of the ith group of round holes; n is n i The number of the circular holes in the ith group; Δp is the pressure difference of the fluid flowing through the long l round tube; q is the main piston flow;
the differential pressure between two ends of the main piston in the first stage is calculated as follows:
wherein m is the flow index; k is the consistency coefficient; l is the width of the piston, namely the length of the circular tube; s is that the piston is provided with s groups of round holes with different apertures; r is R i Is the radius of the ith group of round holes; n is n i The number of the circular holes in the ith group; Δp is the pressure difference of the fluid flowing through the long l round tube; q is the main piston flow;
the first stage master piston aperture damping force is calculated as follows:
wherein m is a flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the diameter of the piston rod; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; d, d i Is the diameter of the ith group of round holes; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the position from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stageIs a distance of (3).
Optionally, the secondary piston pore flow and gap flow rates of the transition section are as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; Δp is the pressure difference across the secondary piston; q is flow;
the differential pressure between the two ends of the secondary piston of the transition section is calculated as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; Δp piston differential pressure across; q is flow;
the secondary piston damping force is calculated as follows:
the transition section damping force is equal to the superposition of the primary piston damping force and the secondary piston damping force:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; d is the diameter of the piston rod; d, d i Is the diameter of the ith group of round holes; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; q is the flow.
Optionally, the secondary piston aperture flow and gap flow rates of the second stage are as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; v is the piston movement speed; h is the gap height; Δp piston differential pressure across; q is flow;
the differential pressure across the secondary piston of the second stage is calculated as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; v is the piston movement speed; h is the gap height; Δp piston differential pressure across; q is flow;
the second stage secondary piston damping force is calculated as follows:
the damping force of the second stage is equal to the superposition of the primary piston and the secondary piston:
Wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; d is the diameter of the piston rod; d, d i Is the diameter of the ith group of round holes; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; q is the flow.
Optionally, the method further comprises:
calculating damping coefficients of each stage according to the damping force of the viscous damper of the first stage, the transition stage or the second stage;
and carrying out component parameter design on the double-order viscous damper according to the damping coefficient and the damping design target of each stage.
Optionally, the damping coefficients of the stages are as follows:
optionally, the step of performing component parameter design on the dual-order viscous damper according to the damping coefficient and the damping design target of each stage includes: determining a target damping coefficient and a target damping index according to the damping design target; the target damping coefficient comprises a first-order damping coefficient and a second-order damping coefficient; and carrying out component parameter design on the double-order viscous damper according to the target damping coefficient and the target damping index.
Optionally, the characteristics affecting the first-order damping coefficient include diameter, number, master piston diameter, master piston width, piston rod diameter, master cylinder inner diameter, flow index and consistency coefficient of the damping fluid on the master piston; the characteristics affecting the second-order damping coefficient comprise the diameter, the number, the secondary piston diameter, the secondary piston width, the piston rod diameter, the secondary cylinder inner diameter, the distance between the inner wall of the secondary cylinder and the secondary piston, the flow index and the consistency coefficient of damping fluid of the secondary piston besides the characteristics of the primary piston.
Optionally, a transition damping coefficient is also included; the characteristics affecting the transition damping coefficient comprise the diameter, the number, the secondary piston diameter, the secondary piston width, the piston rod diameter, the secondary cylinder inner diameter, the distance between the inner wall of the secondary cylinder and the secondary piston, the flow index and the consistency coefficient of damping fluid and the relative displacement relation between the secondary piston and the variable cross section of the secondary cylinder besides the characteristics of the primary piston.
The embodiment of the invention provides a damping force prediction system of a dual-order viscous damper, wherein when a damper secondary piston of the dual-order viscous damper is in a first stage, damping force comprises a primary piston pore flow damping force; when the secondary piston of the damper is positioned in the transition section, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, wherein the secondary piston gap flow damping force is related to the position and the movement speed of the secondary piston; after the secondary piston of the damper completely enters the second stage, the damping force comprises a primary piston aperture flow damping force, a secondary piston gap flow damping force and an aperture flow damping force, wherein the secondary piston gap flow damping force is only related to the movement speed of the secondary piston; the system comprises:
The first damping force calculation module is used for acquiring the pore flow rate of the main piston in the first stage and calculating the pressure difference of the two ends of the main piston in the first stage according to the pore flow rate of the main piston; calculating a damping force of a hole of the main piston according to the pressure difference between two ends of the main piston at the first stage, and taking the damping force as a damping force of the viscous damper at the first stage; or,
the second damping force calculation module is used for acquiring the pore flow rate of the main piston in the transition section and the second stage, simultaneously acquiring the sum of the pore flow rate of the secondary piston and the gap flow rate, calculating the pressure difference at two ends of the main piston according to the pore flow rate of the main piston, and calculating the pressure difference at two ends of the secondary piston according to the sum of the pore flow rate of the secondary piston and the gap flow rate; and calculating a primary piston damping force according to the differential pressure between two ends of the primary piston, calculating a secondary piston damping force according to the differential pressure between two ends of the secondary piston, and taking the sum of the primary piston pore damping force and the secondary piston damping force as the viscous damper damping force of the transition section or the second stage.
The method and the system for predicting the damping force of the dual-order viscous damper provided by the embodiment of the invention comprise the first-stage damping force predicting method, the transition-stage damping force predicting method and the second-stage damping force predicting method, so that the damping force of the dual-order viscous damper can be effectively predicted, and compared with the damping force calculated by directly utilizing the traditional calculation method of superposition of the damping force of the viscous damper, the damping force calculated by the method is more accurate, and the structural seismic response analysis of the dual-order viscous damper can be effectively developed.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present invention, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.
FIG. 1 is a schematic cross-sectional view of a dual-stage viscous damper according to an embodiment of the present invention;
FIG. 2 is a schematic cross-sectional view of a secondary piston of a dual-stage viscous damper according to an embodiment of the present invention;
FIG. 3 is a flow chart of a method for predicting damping force of a dual-order viscous damper according to an embodiment of the present invention;
FIG. 4 is a schematic diagram of a first stage of the secondary piston movement of a dual-stage viscous damper according to an embodiment of the present invention;
FIG. 5 is a schematic illustration of a secondary piston motion transition of a dual-stage viscous damper according to an embodiment of the present invention;
FIG. 6 is a schematic diagram of a second stage of motion of a secondary piston of a dual-stage viscous damper according to an embodiment of the present invention;
FIG. 7 is a flow chart of another method for predicting damping force of a dual-order viscous damper according to an embodiment of the invention;
FIG. 8 is a graph of damping force versus displacement hysteresis for a dual-order viscous damper in accordance with an embodiment of the present invention;
Fig. 9 is a schematic structural diagram of a dual-order viscous damper damping force prediction system according to an embodiment of the present invention.
Detailed Description
In order that the above objects, features and advantages of the invention will be readily understood, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the invention.
The traditional single-order viscous damper structure consists of a cylinder barrel, a piston, viscous fluid, a piston rod and the like, wherein the cylinder barrel is filled with the viscous fluid, the piston can reciprocate in the cylinder barrel under the drive of the piston rod, and a proper amount of small holes are formed in the piston. When the structure is deformed to enable the cylinder barrel and the piston to move relatively, viscous fluid is forced to flow through the small hole under the action of pressure difference, so that damping force is generated, vibration energy is consumed through viscous energy consumption, and the purposes of energy dissipation and vibration reduction are achieved.
At present, the mechanical formula of the traditional single-order viscous damper comprises the following steps: f=cv α
The damping index is mainly obtained by damping fluid characteristics, and aiming at the performance parameter of the damping coefficient C, a calculation method of the pore type viscous damper is already available at present, so that the method can be used for carrying out deepening design processing on the production-oriented damping coefficient C:
However, the conventional single-order viscous damper cannot meet the higher demands. Then the structure of the viscous damper needs to be changed to meet the requirements of different working states, and the structure and the working mechanism of the dual-order viscous damper are available in the market.
The double-order viscous damper mainly comprises a main cylinder barrel, an auxiliary cylinder barrel, a piston rod, a main piston fixedly sleeved on the piston rod, a secondary cylinder barrel arranged between the main cylinder barrel and the auxiliary cylinder barrel, a secondary piston fixedly sleeved on the piston rod and the like, wherein damping holes are formed in the main piston and the secondary piston. The motion of the piston rod can drive the main piston and the secondary piston to jointly move, and the section of the inner wall of the secondary cylinder barrel is changed, so that the gaps between the secondary piston and the inner wall of the secondary cylinder barrel can be changed in the motion process, and the requirements of different working states are met. The dual-order viscous damper, as shown in fig. 1, is schematically illustrated in cross-section, showing a primary cylinder 1, a primary piston 2, a secondary cylinder 3, a secondary piston 4, and a piston bore 5.
But there is still a need for a dual order viscous damper that addresses the problems:
(1) The restoring force model of the double-order viscous damper is lacking, and the structural seismic response analysis is difficult to develop;
(2) The theory of calculating the performance parameters of the dual-order viscous damper is lacking, and the deep design of the viscous damper is difficult to be carried out aiming at the performance parameters of the viscous damper.
The embodiment of the invention aims at least solving the two problems that in the prior art, a restoring force model of a double-order viscous damper (Viscous Fluid Damper, VFD) is lacked, structural seismic response analysis is difficult to develop, a performance parameter calculation theory of the double-order VFD is lacked, and the VFD is difficult to deeply design aiming at the performance parameters of the VFD.
First, aiming at the first problem (the calculation formula of the damping force of the dual-order viscous damper is not clear, and the purpose of obtaining the damping force of the variable-damping viscous damper according to the damper structure cannot be obtained relatively accurately). The embodiment of the invention provides a method for predicting the damping force of a dual-order viscous damper, which is used for establishing a dual-order viscous damper restoring force model, solving the problem of researching the mechanical property of the dual-order viscous damper and effectively predicting the damping force output of the dual-order viscous damper. Is suitable for various energy dissipation and shock absorption structural systems.
Secondly, aiming at the second problem, the embodiment of the invention provides a calculation theory of the performance parameters of the dual-order viscous damper, and the dual-order viscous damper can be deeply designed according to the performance parameters of the viscous damper required by the building structure so as to adapt to the energy dissipation and shock absorption performance requirements of the building structure in different stress stages.
According to the embodiment of the invention, through the structural characteristics of the double-order viscous damper, the damping force of the damper in different working states can be calculated, the working state of the double-order viscous damper is determined by two parts, the first part is the movement speed of the piston, and the second part is the position of the piston.
The calculation is assumed as follows:
when the damper secondary piston is in the first stage, only the primary piston aperture flows damping force; when the secondary piston is in the transition section, namely the secondary piston is started to completely enter the second stage, the damping force not only has the damping force of the pore flow of the primary piston, but also comprises the gap flow and the pore flow damping of the secondary piston, and at the moment, the damping force of the secondary piston also changes due to the change of the gap flow length of the secondary piston, and is related to the position and the movement speed of the piston; when the secondary piston completely enters the second stage, the gap flow damping force of the primary piston, the gap flow damping force of the secondary piston and the gap flow damping force of the secondary piston exist, and after the secondary piston completely enters the second stage, the gap length between the secondary piston and the cylinder barrel is not changed any more, and at the moment, the secondary piston damping force is only related to the piston movement speed.
The cross-sectional schematic of the secondary piston of the dual-order viscous damper as shown in fig. 2 shows the cylinder 11, the piston 12, and the piston rod 13. The piston diameter D is also shown in FIG. 2 0 An inner diameter D of the cylinder barrel, a diameter D of the piston rod, a clearance height h and a diameter D of the small hole i 。
Referring to fig. 3, a flow chart of a method for predicting damping force of a dual-order viscous damper according to an embodiment of the present invention is shown, where the damping force includes a primary piston pore flow damping force when a secondary piston of the dual-order viscous damper is in a first stage; when the secondary piston of the damper is positioned at the transition section, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, wherein the secondary piston gap flow damping force is related to the position and the movement speed of the secondary piston; after the secondary piston of the damper completely enters the second stage, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, and the secondary piston gap flow damping force is only related to the motion speed of the secondary piston after the secondary piston completely enters the second stage; the method comprises the following steps:
s302, in the first stage, the pore flow rate of the main piston is obtained, and the pressure difference of the two ends of the main piston in the first stage is calculated according to the pore flow rate of the main piston.
S304, calculating the damping force of the hole of the main piston according to the pressure difference of the two ends of the main piston at the first stage, and taking the damping force as the damping force of the viscous damper at the first stage.
The damping force prediction method of the first stage based on the above manner is provided in the present embodiment.
S306, in the transition section and the second stage, obtaining the sum of the pore flow rate of the main piston, the pore flow rate of the secondary piston and the gap flow rate, calculating the pressure difference between two ends of the main piston according to the pore flow rate of the main piston, and calculating the pressure difference between two ends of the secondary piston according to the sum of the pore flow rate of the secondary piston and the gap flow rate.
And S308, calculating a main piston damping force according to the differential pressure at two ends of the main piston, calculating a secondary piston damping force according to the differential pressure at two ends of the secondary piston, and taking the sum of the damping force of the aperture of the main piston and the damping force of the secondary piston as the damping force of the viscous damper in the transition section or the second stage.
In this embodiment, a damping force prediction method based on the transition section and the second stage of the above manner is provided.
The method for predicting the damping force of the dual-order viscous damper provided by the embodiment of the invention comprises the first-stage damping force predicting method, the transition-stage damping force predicting method and the second-stage damping force predicting method, so that the damping force of the dual-order viscous damper can be effectively predicted, and compared with the damping force calculated by directly utilizing the traditional calculation method of superposition of the damping force of the viscous damper, the damping force calculated by the method is more accurate, and the structural earthquake response analysis of the dual-order viscous damper can be effectively developed.
The implementation method and the calculation process are described in detail below.
(1) When the value of the absolute value of x is less than or equal to S, the viscous damper only works in the first stage, only the primary piston has the aperture damping force, and the secondary piston has zero damping force due to the overlarge gap. FIG. 4 is a schematic diagram of a first stage of secondary piston movement of a dual order viscous damper in accordance with an embodiment of the present invention. Fig. 4 shows the piston width l, the distance S from the secondary piston surface to the inner wall of the secondary cylinder at the variable cross section in the balancing phase, and the gap height h.
The first stage main piston aperture flow rate is determined, comprising:
only the main piston aperture flow rate:
wherein: m is the flow index (damping index); k is the consistency coefficient; l is the width of the piston, namely the length of a circular tube (round hole); s is that the piston is provided with s groups of round holes with different apertures; r is R i Is the radius of the ith group of round holes; n is n i The number of the circular holes in the ith group; Δp is the pressure difference of the fluid flowing through the long l round tube; q is the main piston flow;
the method for solving the pressure difference between two ends of the main piston in the first stage comprises the following steps:
pressure difference between two ends of the main piston:
wherein: m is the flow index (damping index); k is the consistency coefficient; l is the width of the piston, namely the length of a circular tube (round hole); s is that the piston is provided with s groups of round holes with different apertures; r is R i Is the radius of the ith group of round holes; n is n i The number of the circular holes in the ith group; Δp is the pressure difference of the fluid flowing through the long l round tube; q is the main piston flow;
solving a first stage viscous damper damping force, i.e., a master piston aperture damping force, comprising:
Q＝A·v
first stage pore flow damping force:
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the diameter of the piston rod; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; d, d i Is the diameter of the ith group of round holes; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage;
(2) When S is less than or equal to |x| is less than or equal to l+S, the secondary piston is positioned at the transition section, and the main piston and the secondary piston of the viscous damper work together at the moment, and the secondary piston has both pore damping force and clearance damping force. FIG. 5 illustrates a schematic diagram of a secondary piston motion transition of a dual order viscous damper in an embodiment of the present invention.
The method for calculating the pore flow rate and the gap flow rate of the piston in the transition section comprises the following steps:
the primary piston has only pore flow damping force, and the secondary piston has both pore flow damping force and gap flow damping force
Secondary piston flow (pore flow superimposed with gap flow):
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i For the number of the ith group of round holesThe method comprises the steps of carrying out a first treatment on the surface of the x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; Δp is the pressure difference across the secondary piston; q is flow;
the method for solving the pressure difference between two ends of the transition section secondary piston comprises the following steps:
differential pressure across the secondary piston:
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; Δp piston differential pressure across; q is flow;
solving the damping force of the transition section viscous damper, namely the superposition of the damping force of the main piston and the damping force of the secondary piston, comprises the following steps:
Secondary piston damping force:
the damping force of the transition section is equal to the superposition of the primary piston and the secondary piston:
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; d is the diameter of the piston rod; d, d i Is the diameter of the ith group of round holes; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is livingPlug movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; q is flow;
(3) When |x| is not less than l+S, the viscous damper completely enters the second stage to work, at the moment, the main piston and the secondary piston of the viscous damper work together, and the secondary piston has both pore damping force and clearance damping force. Fig. 6 shows a schematic diagram of a second stage of motion of a secondary piston of a dual-stage viscous damper according to an embodiment of the present invention, where x is the damper piston displacement, l is the damper piston width, and S is the distance from the secondary piston face to the variable cross section of the inner wall of the secondary cylinder in the balancing stage.
The method for obtaining the sum of the pore flow of the main piston and the pore flow of the secondary piston in the second stage comprises the following steps:
The primary piston has only pore flow damping force, and the secondary piston has both pore flow and gap flow; at this point the secondary piston has completely entered the second stage and the gap length is no longer changing.
Secondary piston flow (pore flow superimposed with gap flow):
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; v is the piston movement speed; h is the gap height; Δp piston differential pressure across; q is flow;
the method for solving the pressure difference between the main piston and the secondary piston in the second stage comprises the following steps:
differential pressure across the secondary piston:
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is alivePlug diameter; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; v is the piston movement speed; h is the gap height; Δp piston differential pressure across; q is flow;
solving the damping force of the second-stage viscous damper, namely superposition of the damping force of the main piston and the damping force of the secondary piston, comprises the following steps:
The primary piston has only a pore flow damping force and the secondary piston has both pore flow and gap flow.
At this point the secondary piston has completely entered the second stage and the gap length is no longer changing.
Secondary piston damping force:
the damping force of the second stage is equal to the superposition of the primary piston and the secondary piston:
wherein: m is the flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; d is the diameter of the piston rod; d, d i Is the diameter of the ith group of round holes; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the displacement from the piston surface to the change position of the section of the secondary cylinder barrel; h is the gap height; q is the flow.
Fig. 7 is a schematic flow chart of a method for predicting damping force of a dual-order viscous damper according to an embodiment of the invention, including the following steps:
1. input piston displacement, velocity
2. And judging the state of the piston.
If |x| is less than or equal to S, then:
3. calculating the first-stage viscous fluid flow; 4. calculating the pressure difference between two ends of the main piston in the first stage; 5. calculating the damping force of the first-stage viscous damper
If S is less than or equal to |x| is less than or equal to l+S, then:
6. calculating the viscous fluid flow of the transition section; 7. calculating the pressure difference between two ends of the transition section piston; 8. calculating the damping force of the viscous damper of the transition section;
If |x| is not less than l+S, then:
9. calculating the viscous fluid flow of the second stage; 10. calculating the pressure difference between two ends of the piston in the second stage; 11. and calculating the damping force of the second-stage viscous damper.
The embodiment of the invention provides a method for predicting the damping force of a dual-order viscous damper and a restoring force model thereof, and provides a theory for calculating the performance parameters of the dual-order viscous damper, wherein the dual-order viscous damper can be deeply designed according to the performance parameters of the viscous damper required by a building structure so as to adapt to the energy dissipation and damping performance requirements of the building structure in different stress stages, and the damping force is calculated as follows:
the relation between the damping force and the damping parameter of the damper can be simplified as follows:
F＝Cv α
the damping coefficients of the three phases are thus:
therefore, the deep design of the dual-order viscous damper can be performed according to the required performance parameters.
The features and capabilities of embodiments of the present invention are described in further detail below in conjunction with the following examples:
for example, there is a sine wave displacement x=asin (2pi ft), where x is the sine wave displacement amplitude; f is sine wave frequency, t is loading time; sine wave displacement amplitude x max The displacement is required to be larger than the second-order complete starting displacement, namely x is larger than or equal to l+S;at this time, under the sine wave displacement loading, the first stage, the transition section and the second stage of the dual-order viscous damper all work. The damping force of these three-part dual-order viscous dampers needs to be predicted.
Aiming at the problems, the embodiment provides a method for predicting the damping force of a dual-order viscous damper, which can accurately predict the damping force according to the structural characteristics of a damping device of the dual-order viscous damper, accords with the actual situation, and has accurate and available data.
First, the method requires the following input conditions:
sine wave displacement x=asin (2pi ft), unit: millimeter (mm)
Corresponding to a velocity v=2pi f a cos (2pi ft), unit: millimeter/second
Flow index (damping index) m
Consistency coefficient k, units: pascals
Diameter D of piston 0 Units: millimeter (mm)
Cylinder bore diameter D, unit: millimeter (mm)
Diameter d of piston rod, unit: millimeter (mm)
Piston width l, unit: millimeter (mm)
Number of open-cell groups on piston s
Diameter d of ith round hole i Units: millimeter (mm)
Radius R of ith group of round holes i Units: millimeter (mm)
Number n of circular holes of the i th group i ，
The distance S from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage is as follows: millimeter (mm)
Gap height h, unit: millimeter (mm)
A method for predicting the damping force of a dual-order viscous damper specifically comprises the following steps:
step one, inputting sine wave displacement x=asin (2pi ft), wherein x is sine wave displacement amplitude; f is sine wave frequency, t is loading time;
Step two, obtaining the speed v of each step according to sine wave displacement, wherein v=2pi f A cos (2pi ft);
step three, calculating damping force of each stage according to a damping force prediction formula of the dual-order viscous damper:
and step four, drawing the damping force and each step of displacement into a damping force-displacement curve according to the damping force obtained by applying sine wave displacement. FIG. 8 illustrates a damping force-displacement hysteresis curve of a dual-order viscous damper in an embodiment of the invention.
Aiming at the problem that the performance parameter calculation theory of the dual-order viscous damper is lacked, and the deep design of the viscous damper is difficult to be carried out aiming at the performance parameter of the viscous damper, the corresponding analysis design steps are provided;
according to the scheme, design calculation can be conducted through the damper structure aiming at the damping coefficient and the damping index value, wherein the damping index can be determined according to a rheological experiment of damping fluid.
For example, a building structure needs to be selected to be subjected to damping design and reinforcement by a proper double-order viscous damper. It is necessary to obtain the performance parameters of the dual-order viscous damper and design the structure thereof in a deepened manner so as to facilitate the subsequent production and processing of the dual-order viscous damper.
The specific design steps are as follows:
step one: and designing the main body structure by utilizing structural design software or by manual calculation to establish an anti-seismic model. According to the regional defense target, combining the earthquake effect with other load effects, and calculating the bearing force earthquake resistance adjustment coefficient to design the cross section of the component; meanwhile, corresponding anti-seismic construction measures are adopted, so that the ductility, the deformability and the energy consumption of the structure are ensured; limiting the displacement angle between elastic and plastic layers of the structure under large earthquake, and carrying out shock absorption design when the traditional earthquake resistance can not meet the requirement.
Step two: determining a damping coefficient and damping indexes (C1, C2 and alpha) of the dual-order viscous damper required for reaching the damping design target according to the required main structure damping design target;
according to the earthquake-resistant model and the structural vibration-resistant design requirement, defining and arranging a double-order viscous damper in structural analysis software, and adjusting the numerical values of a first-order damping coefficient C1, a second-order damping coefficient C2 and a damping index alpha by utilizing the existing subprogram of the double-order viscous damper to perform earthquake response control analysis on the vibration-resistant structure so as to enable the interlayer displacement angle and floor acceleration to reach the design specification requirement.
Step three: according to the scheme, the component parameter design is carried out on the dual-order viscous damper aiming at the required performance parameter of the dual-order viscous damper.
According to the performance parameters of the dual-order viscous damper obtained in the second step, the dual-order viscous damper is deeply designed according to the scheme, namely, the components of the dual-order viscous damper are designed, and proper damping fluid is selected so as to achieve the performance parameters required by design. Thereby achieving the structural shock absorption design goal. The influence of the parameters of the dual-order viscous damper element on the performance parameters of the dual-order viscous damper element in the specific design process is as follows:
the damping coefficients at different stages are:
In the embodiment, the structural parameters of the two pistons can be inconsistent, so that the structural characteristics of the two pistons in the same stage can be adjusted to achieve the characteristic of different damping forces of the main piston and the secondary piston, namely the characteristic of C2/C1, so that the double-order viscous damper can play a role in better dissipating the seismic energy under a large earthquake and achieve the design target.
C1, C2 and alpha are main performance parameters affecting the performance of the dual-order viscous damper, wherein C1, C2 and alpha can be determined according to the structural characteristics of the dual-order viscous damper and the characteristics of damping fluid; the mechanical performance parameters of the damper can be obtained through the combination of different parameter values, so that the dual-order viscous damper required by the building damping structure is achieved.
Wherein the main characteristics affecting C1 are diameter, number, main piston diameter, main piston width, piston rod diameter, main cylinder inner diameter, flow index m and consistency coefficient k of damping fluid of the main piston;
the main characteristics affecting C2 are the diameter, the number, the secondary piston diameter, the secondary piston width, the piston rod diameter, the secondary cylinder inner diameter, the distance between the inner wall of the secondary cylinder and the secondary piston, the flow index m of damping fluid and the consistency coefficient k of the secondary piston besides the main piston characteristics;
C Transition The performance parameters affecting the dual-order viscous damper are further optimized for the method for predicting and calculating the damping force of the dual-order viscous damper, and influence C Transition Besides the main piston characteristics, the main characteristics of the damping fluid comprise the diameter, the number, the secondary piston diameter, the secondary piston width, the piston rod diameter, the secondary cylinder inner diameter, the distance between the inner wall of the secondary cylinder and the secondary piston, the flow index m and the consistency coefficient k of the damping fluid, and meanwhile, the relative displacement relation between the secondary piston and the variable section of the secondary cylinder is also an important judging index.
At present, the existing calculation software cannot specifically analyze and calculate the double-order viscous damper, and the working state of the damper, the speed, the displacement and the output of the damper and the structural relation of the damper cannot be predicted. By using the method, the structural relation between the working state, the speed, the displacement and the output force of the dual-order viscous damper and the dual-order viscous damper can be accurately calculated.
Meanwhile, damping coefficients C1 and C2 of different working stages can be calculated relatively accurately, and model selection design and test verification of the double-order viscous damper in the aspect of a later building structure are facilitated.
According to the embodiment of the invention, the design flow of the damper damping device is perfected by providing the calculation method of the double-order viscous damper, and the damping force can be predicted according to the damper structure. The working process of the dual-order viscous damper and the damping force-displacement hysteresis curve under the changes of the piston speed and different positions can be effectively simulated. The method for calculating the damping force of the double-order viscous damper is optimized.
In a word, this scheme has solved the technical problem of two double-order viscous dampers effectively, includes: (1) The restoring force model of the double-order viscous damper is provided, the structural seismic response analysis (2) of the double-order viscous damper can be effectively developed, the performance parameter calculation theory of the double-order viscous damper is provided, and the deepening design of the viscous damper is facilitated for the performance parameters of the double-order viscous damper.
Compared with the traditional calculation method of the viscous damper, the method for predicting the damping force of the dual-order viscous damper provided by the embodiment of the invention can accurately predict the damping force of the viscous damper when the structure encounters different types and different levels of disasters.
The piston rod drives the piston to move under the displacement loading of the double-order viscous damper, in theory, the double-order viscous damper is formed by connecting two pore type dampers in series, but the transition section entering the second stage in the first stage has errors, so that the actual damping force is smaller than the theoretical value, and the influence of the errors on theoretical calculation is reduced as far as possible.
The embodiment of the invention provides a restoring force model of a double-order viscous damper, which can effectively develop the structural seismic response analysis of the double-order viscous damper; the performance parameter calculation theory of the dual-order viscous damper is provided, and the deep design of the viscous damper is facilitated for the performance parameters of the dual-order viscous damper.
Fig. 9 shows a schematic structural diagram of a dual-order viscous damper damping force prediction system according to an embodiment of the present invention, where the system includes:
a first damping force calculation module 901, configured to obtain a main piston pore flow rate in the first stage, and calculate a differential pressure between two ends of the main piston in the first stage according to the main piston pore flow rate; calculating a damping force of a hole of the main piston according to the pressure difference between two ends of the main piston at the first stage, and taking the damping force as a damping force of the viscous damper at the first stage; or,
a second damping force calculation module 902, configured to obtain a primary piston pore flow rate, a secondary piston pore flow rate, and a gap flow rate in the transition section and the second stage, calculate a differential pressure between two ends of the primary piston according to the primary piston pore flow rate, and calculate a differential pressure between two ends of the secondary piston according to a sum of the secondary piston pore flow rate and the gap flow rate; and calculating a primary piston damping force according to the differential pressure between two ends of the primary piston, calculating a secondary piston damping force according to the differential pressure between two ends of the secondary piston, and taking the sum of the primary piston pore damping force and the secondary piston damping force as the viscous damper damping force of the transition section or the second stage.
The damping force prediction system for the dual-order viscous damper provided by the embodiment of the invention can predict the damping force of the first stage, the transition stage and the second stage, can effectively predict the damping force of the dual-order viscous damper, is more accurate compared with the damping force calculated by directly utilizing the traditional calculation method of superposition of the damping force of the viscous damper, and can effectively develop the structural seismic response analysis of the dual-order viscous damper.
It will be appreciated by those skilled in the art that implementing all or part of the above-described methods in the embodiments may be implemented by a computer level to instruct a control device, where the program may be stored in a computer readable storage medium, where the program may include the above-described methods in the embodiments when executed, where the storage medium may be a memory, a magnetic disk, an optical disk, or the like.
In this document, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
In the present specification, each embodiment is described in a progressive manner, and each embodiment is mainly described in a different point from other embodiments, and identical and similar parts between the embodiments are all enough to refer to each other.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims (10)

1. The method for predicting the damping force of the double-order viscous damper is characterized in that when a damper secondary piston of the double-order viscous damper is in a first stage, the damping force comprises a primary piston pore flow damping force; when the secondary piston of the damper is positioned in the transition section, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, wherein the secondary piston gap flow damping force is related to the position and the movement speed of the secondary piston; after the secondary piston of the damper completely enters the second stage, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, and after the secondary piston completely enters the second stage, the secondary piston gap flow damping force is only related to the movement speed of the secondary piston;
The method comprises the following steps:
in the first stage, acquiring a main piston pore flow rate, and calculating a pressure difference between two ends of the main piston in the first stage according to the main piston pore flow rate;
calculating a damping force of a hole of the main piston according to the pressure difference between two ends of the main piston at the first stage, and taking the damping force as a damping force of the viscous damper at the first stage; or,
in the transition section and the second stage, obtaining a primary piston pore flow rate, a secondary piston pore flow rate and a gap flow rate, calculating a differential pressure at two ends of a primary piston according to the primary piston pore flow rate, and calculating a differential pressure at two ends of a secondary piston according to the sum of the secondary piston pore flow rate and the gap flow rate;
and calculating a primary piston damping force according to the differential pressure between two ends of the primary piston, calculating a secondary piston damping force according to the differential pressure between two ends of the secondary piston, and taking the sum of the primary piston pore damping force and the secondary piston damping force as the viscous damper damping force of the transition section or the second stage.
2. The method of claim 1, wherein the primary piston pore flow rate of the first stage is as follows:
wherein m is the flow index; k is the consistency coefficient; l is the width of the piston, namely the length of the circular tube; s is that the piston is provided with s groups of round holes with different apertures; r is R i Is the radius of the ith group of round holes; n is n i The number of the circular holes in the ith group; Δp is the pressure difference of the fluid flowing through the long l round tube; q is the main piston flow;
the differential pressure between two ends of the main piston in the first stage is calculated as follows:
wherein m is the flow index; k is the consistency coefficient; l is the width of the piston, namely the length of the circular tube; s is that the piston is provided with s groups of round holes with different apertures; r is R i Is the radius of the ith group of round holes; n is n i The number of the circular holes in the ith group; Δp is the pressure difference of the fluid flowing through the long l round tube; q is the main piston flow;
the first stage master piston aperture damping force is calculated as follows:
wherein m is a flow index (damping index); k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the diameter of the piston rod; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; d, d i Is the diameter of the ith group of round holes; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage.
3. The method of claim 2, wherein the secondary piston pore flow and gap flow rates of the transition section are as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; Δp is the pressure difference across the secondary piston; q is flow;
the differential pressure between the two ends of the secondary piston of the transition section is calculated as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the movement of the pistonA speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; Δp piston differential pressure across; q is flow;
the secondary piston damping force is calculated as follows:
the transition section damping force is equal to the superposition of the primary piston damping force and the secondary piston damping force:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; d is the diameter of the piston rod; d, d i Is the diameter of the ith group of round holes; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; q is the flow.
4. The method of claim 2, wherein the secondary piston pore flow and gap flow rates of the second stage are as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; v is the piston movement speed; h is the gap height; Δp piston differential pressure across; q is flow;
the differential pressure across the secondary piston of the second stage is calculated as follows:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; v is the piston movement speed; h is the gap height; Δp piston differential pressure across; q is flow;
The second stage secondary piston damping force is calculated as follows:
the damping force of the second stage is equal to the superposition of the primary piston and the secondary piston:
wherein m is the flow index; k is the consistency coefficient; d (D) 0 Is the diameter of the piston; d is the inner diameter of the cylinder barrel; r is R i Is the radius of the ith group of round holes; l is the width of the piston; d is the diameter of the piston rod; d, d i Is the diameter of the ith group of round holes; s is that the piston is provided with s groups of round holes with different apertures; n is n i The number of the circular holes in the ith group; x is piston displacement; v is the piston movement speed; s is the distance from the secondary piston surface to the variable cross section of the inner wall of the secondary cylinder barrel in the balance stage; h is the gap height; q is the flow.
5. The method according to any one of claims 2-4, further comprising:
calculating damping coefficients of each stage according to the damping force of the viscous damper of the first stage, the transition stage or the second stage;
and carrying out component parameter design on the double-order viscous damper according to the damping coefficient and the damping design target of each stage.
6. The method of claim 5, wherein the damping coefficients of the stages are as follows:
7. the method of claim 5, wherein the step of designing the member parameters of the dual-order viscous damper according to the damping coefficients and the damping design targets of the stages comprises:
Determining a target damping coefficient and a target damping index according to the damping design target; the target damping coefficient comprises a first-order damping coefficient and a second-order damping coefficient;
and carrying out component parameter design on the double-order viscous damper according to the target damping coefficient and the target damping index.
8. The method of claim 7, wherein the step of determining the position of the probe is performed,
the characteristics affecting the first-order damping coefficient comprise the diameter, the number, the diameter, the width, the diameter of the piston rod, the inner diameter of the main cylinder barrel, the flow index and the consistency coefficient of damping fluid of the piston holes on the main piston;
the characteristics affecting the second-order damping coefficient comprise the diameter, the number, the secondary piston diameter, the secondary piston width, the piston rod diameter, the secondary cylinder inner diameter, the distance between the inner wall of the secondary cylinder and the secondary piston, the flow index and the consistency coefficient of damping fluid of the secondary piston besides the characteristics of the primary piston.
9. The method of claim 8, further comprising a transition damping coefficient;
the characteristics affecting the transition damping coefficient comprise the diameter, the number, the secondary piston diameter, the secondary piston width, the piston rod diameter, the secondary cylinder inner diameter, the distance between the inner wall of the secondary cylinder and the secondary piston, the flow index and the consistency coefficient of damping fluid and the relative displacement relation between the secondary piston and the variable cross section of the secondary cylinder besides the characteristics of the primary piston.
10. A dual-order viscous damper damping force prediction system, wherein the damping force comprises a primary piston aperture flow damping force when a damper secondary piston of the dual-order viscous damper is in a first stage; when the secondary piston of the damper is positioned in the transition section, the damping force comprises a primary piston pore flow damping force, a secondary piston gap flow damping force and a pore flow damping force, wherein the secondary piston gap flow damping force is related to the position and the movement speed of the secondary piston; after the secondary piston of the damper completely enters the second stage, the damping force comprises a primary piston aperture flow damping force, a secondary piston gap flow damping force and an aperture flow damping force, wherein the secondary piston gap flow damping force is only related to the movement speed of the secondary piston; the system comprises:
the first damping force calculation module is used for acquiring the pore flow rate of the main piston in the first stage and calculating the pressure difference of the two ends of the main piston in the first stage according to the pore flow rate of the main piston; calculating a damping force of a hole of the main piston according to the pressure difference between two ends of the main piston at the first stage, and taking the damping force as a damping force of the viscous damper at the first stage; or,
the second damping force calculation module is used for acquiring the pore flow rate of the main piston in the transition section and the second stage, simultaneously acquiring the sum of the pore flow rate of the secondary piston and the gap flow rate, calculating the pressure difference at two ends of the main piston according to the pore flow rate of the main piston, and calculating the pressure difference at two ends of the secondary piston according to the sum of the pore flow rate of the secondary piston and the gap flow rate; and calculating a primary piston damping force according to the differential pressure between two ends of the primary piston, calculating a secondary piston damping force according to the differential pressure between two ends of the secondary piston, and taking the sum of the primary piston pore damping force and the secondary piston damping force as the viscous damper damping force of the transition section or the second stage.
CN202311057239.8A 2023-08-21 2023-08-21 Method and system for predicting damping force of double-order viscous damper Active CN117150953B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202311057239.8A CN117150953B (en) 2023-08-21 2023-08-21 Method and system for predicting damping force of double-order viscous damper

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202311057239.8A CN117150953B (en) 2023-08-21 2023-08-21 Method and system for predicting damping force of double-order viscous damper

Publications (2)

Publication Number Publication Date
CN117150953A true CN117150953A (en) 2023-12-01
CN117150953B CN117150953B (en) 2024-06-14

Family

ID=88903673

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202311057239.8A Active CN117150953B (en) 2023-08-21 2023-08-21 Method and system for predicting damping force of double-order viscous damper

Country Status (1)

Country Link
CN (1) CN117150953B (en)

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110017558A1 (en) * 2007-12-14 2011-01-27 Ohlins Racing Ab Shock absorber with increasing damping force
WO2020073220A1 (en) * 2018-10-10 2020-04-16 南华大学 Dualextruding, piezoelectricity and magnetorheological composite and intelligent damper and control method therefor
CN113187842A (en) * 2021-06-07 2021-07-30 震安科技股份有限公司 Multi-stage damping force viscous damper
CN114110071A (en) * 2021-10-11 2022-03-01 江苏鼎吉能源工程技术有限公司 Viscous fluid damper with variable damping coefficient stages
CN115163716A (en) * 2022-07-08 2022-10-11 广州大学 Viscous damper with variable friction damping
CN115855471A (en) * 2022-12-12 2023-03-28 江苏佳力得新材料科技有限公司 Performance test method of viscous damper with variable damping coefficient

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110017558A1 (en) * 2007-12-14 2011-01-27 Ohlins Racing Ab Shock absorber with increasing damping force
WO2020073220A1 (en) * 2018-10-10 2020-04-16 南华大学 Dualextruding, piezoelectricity and magnetorheological composite and intelligent damper and control method therefor
CN113187842A (en) * 2021-06-07 2021-07-30 震安科技股份有限公司 Multi-stage damping force viscous damper
CN114110071A (en) * 2021-10-11 2022-03-01 江苏鼎吉能源工程技术有限公司 Viscous fluid damper with variable damping coefficient stages
CN115163716A (en) * 2022-07-08 2022-10-11 广州大学 Viscous damper with variable friction damping
CN115855471A (en) * 2022-12-12 2023-03-28 江苏佳力得新材料科技有限公司 Performance test method of viscous damper with variable damping coefficient

Non-Patent Citations (3)

* Cited by examiner, † Cited by third party
Title
GANG XU 等: "Review on self-centering damper for seismic resilient building structures", STRUCTURES, 19 May 2023 (2023-05-19) *
WEIZHI XU 等: "Theoretical and experimental investigation on the seismic performance of a novel variable-damping viscous fluid damper", JOURNAL OF BUILDING ENGINEERING, 20 April 2022 (2022-04-20) *
杨珂 等: "间隙式粘滞阻尼器的力学特性分析", 液压与气动, no. 06, 15 June 2020 (2020-06-15) *

Also Published As

Publication number Publication date
CN117150953B (en) 2024-06-14

Similar Documents

Publication Publication Date Title
Miyamoto et al. Limit states and failure mechanisms of viscous dampers and the implications for large earthquakes
Wu et al. Design guidelines for tuned liquid column damper for structures responding to wind
Chen et al. A vertical isolation device with variable stiffness for long-span spatial structures
Herr et al. A shock absorber model using CFD analysis and Easy5
Dimock et al. Quasi-steady Bingham biplastic analysis of electrorheological and magnetorheological dampers
Gao et al. Mathematical Modelling and Computational Simulation of the Hydraulic Damper during the Orifice‐Working Stage for Railway Vehicles
Xu et al. Theoretical and experimental investigation on the seismic performance of a novel variable-damping viscous fluid damper
CN117150953B (en) Method and system for predicting damping force of double-order viscous damper
Mousavi et al. A novel method for efficient design of frame structures equipped with nonlinear viscous dampers by using computational results of cylindrical friction damper
Ghasemi Jouneghani et al. Assessing seismic performance of the elliptic braced moment resisting frame through pushover method
Lindler et al. Quasi-steady Bingham plastic analysis of an electrorheological flow mode bypass damper with piston bleed
Marazzi Semi-active control of civil structures: implementation aspects
Jampole High-friction sliding seismic isolation for enhanced performance of light frame structures during earthquakes
Pfeiffer et al. New hydraulic system modelling
Landi et al. Equivalent viscous damping for the displacement-based seismic assessment of infilled RC frames
Carrera Akutain et al. A parametric damper model validated on a track
Buczkowski et al. Experimental and numerical studies on the development of hysteresis in a shock absorber with a shim disc valve
Chen et al. Response-spectrum-based design method for active base-isolated buildings with viscous dampers and hysteretic dampers
Buczkowski et al. Modelling the shock absorber piston valve using 2-way fluid-structure interaction
JP4556384B2 (en) Seismic isolation control method, seismic isolation control device, and seismic isolation structure
Christian Plane-strain deformation analysis of soil.
CN109630590A (en) A kind of tower vibrationproof viscous damper
CN117807895B (en) Magnetorheological damper control method and device based on deep reinforcement learning
Li et al. Research on deformation of valve slice of automobile shock absorber
Shabani et al. Evaluation of seismic performance factors of special steel moment resisting frames with basement walls

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant