CN113309809B - Damping device and design method thereof - Google Patents

Damping device and design method thereof Download PDF

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Publication number
CN113309809B
CN113309809B CN202110394013.1A CN202110394013A CN113309809B CN 113309809 B CN113309809 B CN 113309809B CN 202110394013 A CN202110394013 A CN 202110394013A CN 113309809 B CN113309809 B CN 113309809B
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friction
force
shock absorber
damping
outer ring
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CN113309809A (en
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程永锋
林森
卢智成
李圣
朱祝兵
刘振林
孟宪政
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China Electric Power Research Institute Co Ltd CEPRI
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China Electric Power Research Institute Co Ltd CEPRI
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F13/00—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs
    • F16F13/005—Units comprising springs of the non-fluid type as well as vibration-dampers, shock-absorbers, or fluid springs comprising both a wound spring and a damper, e.g. a friction damper
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/04—Friction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2222/00—Special physical effects, e.g. nature of damping effects
    • F16F2222/10—Adhesion
    • 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

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  • Physics & Mathematics (AREA)
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  • Theoretical Computer Science (AREA)
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  • General Physics & Mathematics (AREA)
  • Evolutionary Computation (AREA)
  • Computer Hardware Design (AREA)
  • Pure & Applied Mathematics (AREA)
  • Mathematical Optimization (AREA)
  • Mathematical Analysis (AREA)
  • Computational Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Vibration Dampers (AREA)
  • Vibration Prevention Devices (AREA)

Abstract

The invention provides a damping device and a design method thereof, wherein the damping device comprises the following steps: a support mechanism (10) and a plurality of shock absorbers (11); the shock absorber (11) comprises a shell, an energy dissipation element, an elastic piece and a transmission shaft (3) which sequentially penetrates through the shell and the elastic piece, wherein the energy dissipation element and the elastic piece are positioned in the shell; the supporting mechanism (10) is arranged in the middle of the bottom of the electrical equipment (12), and the shock absorbers (11) are fixed to the electrical equipment (12) through the transmission shaft (3). The invention dissipates the earthquake energy by the work of the energy dissipation element, and gains the damping effect; after the earthquake action disappears, the elastic piece can help the electric equipment (12) to restore the initial state.

Description

Damping device and design method thereof
Technical Field
The invention relates to an anti-seismic safety protection technology for an electric power facility, in particular to a damping device and a design method of the damping device.
Background
Because the energy base and the electric load are not distributed uniformly, a large number of power transformation (converter) stations need to be built in an earthquake-resistant unfavorable area with high earthquake intensity. More than 60% of key equipment in the power transformation (converter) station is pillar type electrical equipment (12) (circuit breakers, transformers and the like), the equipment is usually made of porcelain materials for ensuring the insulating performance, the equipment structure is thin and high for meeting the requirement of electrical gaps, and the design and manufacture are difficult to give consideration to the anti-seismic performance, so the pillar type equipment is seriously damaged by earthquake.
The traditional damping device dissipates the seismic energy transmitted into the electrical equipment (12) during an earthquake, but the damping device cannot automatically reset after the earthquake, residual deformation exists, and the post equipment can accumulate inclination, deflection and other adverse effects after multiple earthquakes or aftershocks. In recent years, friction type damping devices which can be reset after an earthquake also appear, but the damping effect of the damping devices is weak.
Disclosure of Invention
In order to solve the problems that the traditional damping device dissipates the seismic energy transmitted into the electrical equipment (12) during the earthquake, but the damping device cannot automatically reset after the earthquake and has residual deformation, the invention provides the damping device which comprises a supporting mechanism (10) and a plurality of dampers (11);
the shock absorber (11) comprises a shell, an energy dissipation element, an elastic piece and a transmission shaft (3) which sequentially penetrates through the shell and the elastic piece, wherein the energy dissipation element and the elastic piece are positioned in the shell;
the supporting mechanism (10) is arranged in the middle of the bottom of the electrical equipment (12), and the shock absorbers (11) are fixed to the electrical equipment (12) through the transmission shaft (3).
Preferably, the elastic member comprises a spring (5) and a sliding plate, and the middle part of the sliding plate is provided with a hole for the transmission shaft (3) to pass through;
the sliding plates are arranged at two ends of the spring (5).
Preferably, the housing comprises: an outer cylinder (1) and two end covers (2);
two ends of the outer cylinder (1) are respectively connected with the end covers (2);
the energy dissipation elements are arranged on the inner sides of the two end covers (2).
Preferably, the energy consuming element comprises: a damping member.
Preferably, the energy consuming element comprises: a friction assembly (4).
Preferably, the energy consuming element comprises: a friction assembly (4) and a damping member;
the transmission shaft (3) penetrates through the friction component (4) and the damping piece.
Preferably, the friction assembly (4) comprises: a multi-segment outer ring segment and an inner ring (9);
the multiple sections of outer ring sections are sequentially connected to form an outer ring (8); the inner ring (9) is a circular ring with an external conical surface;
the inner conical surface of the outer ring (8) is attached to the outer conical surface of the inner ring (9).
Preferably, the combined form of the outer ring (8) and the inner ring (9) comprises: a first combination form consisting of a pair of single-cone inner rings (9) and an outer ring (8);
a second combination form formed by overlapping a plurality of pairs of single-cone inner rings (9) and outer rings (8);
a third combination form consisting of two single-conical inner rings (9) and a double-conical outer ring (8);
or a fourth combination form consisting of two single-conical-surface inner rings at two ends, n double-conical-surface inner rings in the middle and n +1 groups of double-conical-surface outer rings.
Preferably, the damping member includes: a damping cylinder (7), a viscoelastic element (6) and a strut inside the damping cylinder (7);
one end of the strut is connected with the damping cylinder (7), and the other end of the strut is connected with the end cover (2);
the viscoelastic element (6) has a height smaller than the height of the damping cylinder (7);
the height of the damping cylinder (7) is smaller than that of the spring when the spring compression amount is maximum.
Preferably, the diameter of the upper end surface and the lower end surface of the inner ring (9) is larger than that of the damping cylinder (7), the inner ring is provided with a hole for the support to pass through, and the sliding plate is also provided with a hole for the support to pass through.
Preferably, the method further comprises the following steps: a collar;
the collar is arranged on the upper part of the transmission shaft (3), the lower end face of the collar is in contact with the friction component (4), and the upper end face of the collar is in contact with a flange of the electrical equipment (12).
Based on the same inventive concept, the invention also provides a damping device design method, which comprises the following steps:
determining the position and number of the shock absorbers (11) on the basis of the parameters of the electrical equipment (12) arranged on the support mechanism (10);
determining a design trigger force for each shock absorber (11) based on parameters and seismic fortification requirements of the electrical equipment (12) and the location and number of the shock absorbers (11);
determining the type of shock absorber (11) from the design trigger force of said shock absorber (11);
wherein the type of the shock absorber (11) is determined by the energy dissipation element adopted by the shock absorber (11) and the elastic member matched with the energy dissipation element; the design trigger force is determined by the force generated by a transmission shaft (3) of the shock absorber (11) which sequentially penetrates through the shell and the elastic piece and drives a dissipative element positioned inside the shell of the shock absorber (11) to move in an earthquake.
Preferably, the energy consumption element includes: a damping member and/or a friction assembly.
Preferably, the shock absorbers are of the type comprising:
when the energy dissipation element is a damping part, the damping part and the elastic part form a shock absorber;
when the energy dissipation element is a friction component (4), the shock absorber is composed of the friction component (4) and an elastic component determined by the relation between the spring reaction force and the friction component (4);
when the energy dissipation elements are a damping piece and a friction component (4), the shock absorber is composed of the friction component (4), the damping piece and an elastic piece determined by the relation between the spring reaction force and the friction component (4).
Preferably, the design trigger force is determined by the force generated by the damper (11) transmission shaft (3) sequentially passing through the housing and the elastic member to drive the energy dissipation element inside the housing of the damper (11) to move in the earthquake, and comprises:
when the shock absorber is of the type formed by the damping piece and the elastic piece, the design trigger force is determined by the output force generated by the movement of the viscoelastic element of the damping piece relative to the transmission shaft (3) in the earthquake of the transmission shaft (3);
when the shock absorber is of the type consisting of the friction assembly (4) and an elastic member determined by the relationship of the spring reaction force to the friction assembly (4), the triggering force is designed to be a force that drives the outer ring (8) of the friction assembly (4) in different combinations relative to the housing in an earthquake by the transmission shaft (3);
when the shock absorber is of the type consisting of said friction assembly (4), a damping member and an elastic member defined by the relationship between the spring reaction and said friction assembly (4), the design triggering force is determined by the force exerted by the drive shaft (3) in an earthquake by the movement of the viscoelastic element of said damping member relative to the drive shaft (3), and the force exerted by the outer ring (8) of the friction assembly (4) in different combinations moving relative to the housing.
Preferably, the force of the movement of the outer ring (8) of the friction assembly (4) in relation to the housing in said different combinations is obtained by multiplying the loading stiffness of the shock absorber by the precompression of the elastic member.
Preferably, the friction assembly (4) comprises, in combination:
a first combination form consisting of a pair of single-cone inner rings (9) and an outer ring (8);
a second combination form formed by overlapping a plurality of pairs of single-cone inner rings (9) and outer rings (8);
a third combination form consisting of two single-conical inner rings (9) and a double-conical outer ring (8);
or a fourth combination form consisting of two single-conical-surface inner rings at two ends, n double-conical-surface inner rings in the middle and n +1 groups of double-conical-surface outer rings.
Preferably, the loading stiffness and the unloading stiffness of the friction pack (4) when in the first combination and the second combination are calculated as follows:
Figure BDA0003017874360000041
in the formula, klThe loading stiffness of the shock absorber; theta is the taper angles of the inner ring and the outer ring; k is a radical ofsIs the spring rate; mu.s1: the friction coefficient between the inner ring and the outer ring; mu.s2: coefficient of friction between the outer ring and the housing; n is the number of inner rings and outer rings;
Figure BDA0003017874360000042
in the formula, kuIs the unload stiffness of the shock absorber.
Preferably, the loading stiffness and the unloading stiffness when the friction pack (4) is in the third combination and the fourth combination are calculated as follows:
Figure BDA0003017874360000043
in the formula, klThe loading stiffness of the shock absorber; theta is the taper angles of the inner ring and the outer ring; k is a radical ofsIs the spring rate; mu.s1: the friction coefficient between the inner ring and the outer ring; mu.s2: coefficient of friction between the outer ring and the housing; n is the number of inner rings and outer rings;
Figure BDA0003017874360000044
in the formula, kuIs the unload stiffness of the shock absorber.
Preferably, the damping member output force is calculated according to the following formula:
Figure BDA0003017874360000045
in the formula, f: a viscoelastic element force; k': storing the stiffness; u: displacement of the viscoelastic element;
Figure BDA0003017874360000046
a viscoelastic element speed; eta: a loss factor; and omega represents the excitation frequency.
Compared with the prior art, the invention has the beneficial effects that:
1. the present invention provides a shock absorbing device, comprising: a support mechanism (10) and a plurality of shock absorbers (11); the shock absorber (11) comprises a shell, an energy dissipation element, an elastic piece and a transmission shaft (3) which sequentially penetrates through the shell and the elastic piece, wherein the energy dissipation element and the elastic piece are positioned in the shell; the supporting mechanism 10 is arranged in the middle of the bottom of the electrical equipment (12), and the plurality of shock absorbers (11) are fixed on the electrical equipment (12) through the transmission shaft (3). The invention dissipates the earthquake energy by the work of the energy dissipation element, and gains the damping effect; after the earthquake action disappears, the elastic piece can help the electric equipment (12) to restore the initial state.
2. The invention provides a design method of a damping device, which comprises the following steps: determining the position and number of the shock absorbers (11) on the basis of the parameters of the electrical equipment (12) arranged on the support mechanism (10); determining a design trigger force for each shock absorber (11) based on parameters and seismic fortification requirements of the electrical equipment (12) and the location and number of the shock absorbers (11); determining the type of shock absorber (11) from the design trigger force of said shock absorber (11); wherein the type of the shock absorber (11) is determined by the energy dissipation element adopted by the shock absorber (11) and the elastic member matched with the energy dissipation element; the design trigger force is determined by the force generated by a transmission shaft (3) of the shock absorber (11) which sequentially penetrates through the shell and the elastic piece and drives a dissipative element positioned inside the shell of the shock absorber (11) to move in an earthquake. Compared with the design of the existing damping device, the damping device has the advantages that the energy dissipation elements are determined according to the design trigger force of each damper (11), so that the determined energy dissipation elements can better dissipate seismic energy, the damping effect is enhanced, and meanwhile, the elastic parts matched with the energy dissipation elements are designed, so that the electrical equipment can be reset after the earthquake.
3. The invention can reasonably set the trigger force of the device, ensures that the electrical equipment cannot malfunction under the action of external force such as strong wind, mechanical operation and the like, and can be triggered to work only when an earthquake exceeding the shock resistance of the equipment occurs, thereby protecting the safe and stable operation of the electrical equipment.
4. According to the technical scheme provided by the invention, when the energy dissipation element is the combination of the friction component and the damping element, the problem of weak effect of a single energy dissipation mode is avoided, and the damping effect is enhanced.
Drawings
FIG. 1 is a schematic view of the self-restoring shock absorbing device of the present invention;
FIG. 2 is a schematic view of the internal structure of the self-restoring shock absorber 11 of the present invention
FIG. 3 is a top plan view of an assembled view of form 1 of the friction pack of the present invention;
FIG. 4 is an assembled view of friction pack form 1 of the present invention;
FIG. 5 is a combination view of form 2 of the friction pack of the present invention;
FIG. 6 is a combination view of form 3 of the friction pack of the present invention;
FIG. 7 is a combination view of form 4 of the friction pack of the present invention;
FIG. 8 is a graph of spring and friction element hysteresis according to the present invention;
FIG. 9 is a force analysis diagram of the single cone friction pack of the present invention;
FIG. 10 is a force analysis diagram of the multi-cone friction pack of the present invention;
FIG. 11 is a graph of hysteresis for a viscoelastic element of the present invention;
FIG. 12 is a view showing a shock-absorbing device of the present invention, which is constituted by a damping member and an elastic member;
FIG. 13 is a force-displacement curve of the spring-friction assembly of the present invention;
FIG. 14 is a shock absorbing device of the present invention comprising a friction member and an elastic member;
the device comprises an outer cylinder 1, an end cover 2, a transmission shaft 3, a friction component 4, a spring 5, a viscoelastic element 6, a damping cylinder 7, an outer ring 8, an inner ring 9, a supporting mechanism 10, a shock absorber 11, an electrical device 12 and a device support 13.
Detailed Description
The invention discloses a damping device with a self-recovery function, which can recover the initial state after the earthquake action disappears, and the protected strut-type equipment can not accumulate the adverse effects of inclination, deflection and the like due to the residual deformation of the damping device after the earthquake. The damping device dissipates seismic energy through two mechanisms of friction and viscoelastic damping, the larger the vibration amplitude is, the larger the friction force is, the more the energy consumption is, the faster the device action speed is, and the larger the viscoelastic damping force is. The two energy dissipation mechanisms act together to increase the shock absorption effect, reduce the seismic energy transmitted into the electrical equipment 12, and avoid the problem of weak energy dissipation effect of a single mechanism.
The design method of the device provided by the invention has the advantages that the working principle of the device is clear, the design is easy, and the engineering application is convenient. Through design calculation, the trigger force of the device can be reasonably set, the electrical equipment 12 is guaranteed not to malfunction under the action of external force such as strong wind and mechanical operation, the external force exceeds the starting limit value of the device under the action of a certain grade of earthquake, the device is triggered, the earthquake energy is consumed through friction and viscoelastic damping in work, the shock absorption device can realize self-recovery after the earthquake, and the structure is recovered to the initial state. The damping device is compact in structure, low in cost, easy to machine and assemble, friendly in installation interface, and free of excessive change of the original connection design of the electrical equipment 12 and the support when the conventional electrical equipment 12 is additionally installed.
Example 1: a shock absorbing device, as shown in fig. 1, comprising: a support mechanism 10 and a plurality of dampers 11;
the shock absorber 11 comprises a shell, an energy dissipation element, an elastic element and a transmission shaft 3, wherein the energy dissipation element and the elastic element are positioned in the shell, and the transmission shaft 3 sequentially penetrates through the shell and the elastic element;
the supporting mechanism 10 is arranged in the middle of the bottom of the electrical equipment 12, and the plurality of shock absorbers 11 are fixed on the electrical equipment 12 through the transmission shaft 3;
the plurality of shock absorbers 11 are fixed to the bracket through the housing.
Preferably, the elastic member comprises a spring and a sliding plate, the middle part of the sliding plate is provided with a hole for the transmission shaft 3 to pass through;
the spring is sleeved outside the damping piece;
the sliding plate is provided with two ends of the spring.
Preferably, the housing comprises: an outer cylinder 1 and two end covers 2;
two ends of the outer cylinder 1 are respectively connected with the end covers 2; the energy dissipation elements are arranged inside the two end caps 2.
Preferably, the energy consuming element comprises: a damping member, as shown in fig. 12.
Preferably, the energy consuming element comprises: the friction member 4, as shown in fig. 14.
Preferably, the energy consuming element comprises: a friction assembly 4 and a damping member;
the transmission shaft 3 passes through the friction member 4 and the damper.
Preferably, the friction assembly 4 comprises: a multi-segment outer ring segment and an inner ring 9;
the multiple sections of outer ring sections are sequentially connected to form an outer ring 8; the inner ring 9 is a circular ring with an outer conical surface;
the inner conical surface of the outer ring 8 is attached to the outer conical surface of the inner ring 9;
the inner rings 9 each include: an outer conical surface ring.
Preferably, the combination of the outer ring 8 and the inner ring 9 comprises: a first combination form composed of a pair of single-cone inner rings 9 and an outer ring 8;
a second combination form formed by overlapping a plurality of pairs of single conical surface inner rings 9 and outer rings 8;
a third combination form consisting of two single-conical inner rings 9 and a double-conical outer ring 8;
or a fourth combination form consisting of two single-conical-surface inner rings at two ends, n double-conical-surface inner rings in the middle and n +1 groups of double-conical-surface outer rings.
Preferably, the damping member includes: a damping cylinder 7, a viscoelastic element 6 and a strut inside said damping cylinder 7;
one end of the strut is connected with the damping cylinder 7, and the other end of the strut is connected with the end cover 2;
the viscoelastic element 6 has a height smaller than the height of the damping cylinder 7.
Preferably, the damping cylinder 7 is closed at the bottom and open at the top; the height of the damping cylinder 7 is smaller than that of the spring when the spring is compressed to the maximum.
Preferably, the inner ring 9 has a diameter greater than that of the damping cylinder 7 and has holes for the passage of the struts, and the sliding plate also has holes for the passage of the struts.
Preferably, the method further comprises the following steps: a collar;
the collar is disposed on the upper portion of the drive shaft 3, and the lower end face of the collar is in contact with the friction member 4, and the upper end face of the collar is in contact with the flange of the electrical device 12.
Preferably, the outer ring 8 is made of wear-resistant material.
Example 2:
(1) shock-absorbing device
As shown in fig. 1, the damping device is installed between the device and its support when used in the electrical device 12. A supporting mechanism 10 is fixed at the center of the top plate of the support at the top of the support through welding or bolts, the electrical equipment 12 falls on the supporting mechanism 10, and the supporting mechanism 10 is preferably a cylinder. The shock absorbers 11 are arranged on the outer ring of the supporting mechanism 10, the number of the shock absorbers 11 is preferably the same as that of mounting holes of a bottom flange of the electrical equipment 12, and the diameter of a bolt rod of the shock absorber 11 is preferably matched with that of an opening of the bottom flange of the electrical equipment 12. The shock absorber 11 body passes through a support top plate opening hole, the outer cylinder wall of the shock absorber 11 is provided with threads, and the shock absorber 11 and the support are fixed through an upper special nut and a lower special nut of the support top plate. The transmission shaft 3 of each shock absorber 11 passes through the bottom flange hole of the equipment and is connected with the bottom flange of the equipment through a nut, and the nut is preferably matched with an elastic pad or a double nut to prevent looseness.
When electrical equipment 12 does not choose damping device to carry out conventional installation, electrical equipment 12 directly falls on the support roof, through bolted connection, and chose this damping device for use after, only need expand to 11 ware body sizes of bumper shock absorbers with support roof trompil diameter, do not change original installation arrangement form, only add this bumper shock absorber 11 and supporting mechanism 10 between electrical equipment 12 and support can.
(2) Damper 11 structure
The internal structure of the damper 11 is shown in fig. 2, and the upper and lower end caps 2 and the outer cylinder 1 of the damper 11 enclose the internal components therein. The transmission shaft 3 passes through the friction components 4 at the upper end and the lower end. Spring 5 is pressed from both sides between upper and lower two sets of friction pack 4, and spring 5 can be belleville spring, cylindrical helical compression spring, rectangular cross section cylindrical helical compression spring etc. chooses for use according to exerting oneself size and size during the design. A damping cylinder 7 is arranged in the spring 5, the transmission shaft 3 penetrates through the damping cylinder 7, and the viscoelastic element 6 is bonded between the transmission shaft 3 and the damping cylinder 7 and is made of a viscoelastic material. The end face of the damping cylinder 7 is provided with a support which is connected with the inner surface of the end cover 2 and limits the damping cylinder 7 to move up and down. The 3 upper portions of transmission shaft are equipped with the axle collar, and the terminal surface contacts with friction pack 4 under the axle collar, and the axle collar up end contacts to 12 end flanges of electrical equipment, and 3 lower parts of transmission shaft are equipped with the thread end, compress tightly friction pack 4 through the nut, press spring 5 to initial precompression state, should select for use double nut locking.
The friction pack 4 may have a variety of combinations as shown below:
the friction assembly 4 may have the following form according to design requirements:
(1) a first combination: a pair of single cone inner and outer rings as shown in fig. 3 and 4. The equipment is small in size and light in weight, and the mode can be selected when the requirement on restoration after earthquake is high.
(2) A second combination: a plurality of pairs of single conical surface inner rings and single conical surface outer rings are overlapped, as shown in fig. 5, the friction assembly in the overlapping mode (1) can increase the output force and enhance the friction energy consumption effect.
(3) A third combination: the spring is composed of two single-cone inner rings and a double-cone outer ring, and as shown in fig. 6, the friction force is larger than that of the form (1), but the resilience force of the spring is required to be stronger.
(4) A fourth combination: the friction force can be further increased on the basis of the form (3) as shown in fig. 7. The outer ring of the friction component 4 can be made of common friction pair materials such as brass, bronze, various alloy steels and the like. The inner wall of the outer cylinder 1 may be specially treated to enhance wear resistance and ensure stable frictional characteristics.
The following is a detailed description of the friction assembly in a first combination:
the friction member 4 of the first combination, as shown in fig. 3 and 4, the friction member 4 of the first combination is composed of an outer ring 8 and an inner ring 9. The inner ring 9 is a complete outer conical surface circular ring, the outer ring is formed by m outer ring sections, m is more than or equal to 2, m takes 3 as an example, the m outer ring sections can be spliced into a whole ring, and the whole ring is an inner conical surface circular ring. The inner conical surface of the outer ring 8 and the outer conical surface of the inner ring 9 are jointed to form a friction assembly. The outer ring of the friction component 4 can be made of common friction pair materials such as brass, bronze, various alloy steels and the like. The inner wall of the outer cylinder 1 of the damper 11 may be specially treated to enhance wear resistance and ensure stable frictional characteristics.
(3) Working principle of shock absorber 11
After the shock absorber 11 is assembled, the spring 5 is in a compressed state in an initial state, when the equipment normally works or is subjected to small external force, because the spring 5 has initial pre-pressure of the spring, the outer ring 8 and the inner wall of the outer cylinder 1 are always kept under pressure under the action of axial pre-tightening force, and the external force is not enough to overcome static friction force between the inner wall of the outer cylinder 1 and the outer ring 8, the initial pre-pressure of the spring 5 and damping force generated by a damping piece, the shock absorber 11 cannot be triggered.
When an earthquake of a certain level occurs, an external force overcomes the internal force trigger device of the damping device, the electrical equipment 12 shakes back and forth, the bottom flange of the electrical equipment 12 makes lever motion by taking the supporting mechanism 10 as a fulcrum to drive the transmission shaft 3 of the damper 11 to pull and press up and down, the inner ring 9 of the friction assembly 4 pushes the outer ring 8 under the action of the axial force of the spring 5, so that pressure is generated between the outer ring 8 and the inner wall of the outer cylinder 1, and meanwhile, the outer circle surface of the outer ring 8 and the inner wall of the outer cylinder 1 rub to dissipate earthquake energy in the up and down movement process of the transmission shaft 3. When the transmission shaft 3 moves up and down, the friction component 4 is driven to work, the viscoelastic element 6 of the damping piece is driven to work, the damping cylinder 7 is limited and fixed by the support, and the transmission shaft 3 moves up and down, so that dislocation continuously occurs on the inner side and the outer side of the viscoelastic element 6, damping is generated through shearing deformation of the viscoelastic element 6, and seismic energy is consumed.
When the earthquake stops, the external force borne by the shock absorber 11 disappears, if the shock absorber 11 has residual deformation, namely the transmission shaft 3 is not at the initial position, at the moment, the resilience force of the spring 5 overcomes the friction force between the outer ring 8 and the inner wall of the outer cylinder 1, the damping force of the viscoelastic element 6 and the overturning force generated by the inclination of the electrical equipment 12, and the transmission shaft 3 is pushed back to the original position.
The working effect of the damper 11 can be seen as a combined action of the working effects of the friction member 4 and the visco-elastic element 6. When only the working effects of the spring 5 and the friction member 4 are analyzed, the hysteresis curve is as shown in fig. 8, when the external force is small, the mechanical behavior of the damper 11 is in the OA section, at this time, the damper 11 is not triggered, and the static friction force between the outer ring 8 and the inner wall of the outer cylinder 1 increases as the external force increases. When the external force continues to increase to reach the design trigger force of the device, the maximum static friction force and the spring pre-tightening force inside the shock absorber 11 can be overcome, and the push-pull transmission shaft 3 starts the loading process, as shown in the section AB in the figure. In the loading process, the friction force between the outer ring 8 and the inner wall of the outer cylinder 1 is increased along with the increase of the compression amount of the spring 5, the output force of the spring 5 and the friction component 4 is equal to the sum of the resilience force of the spring and the friction force of the friction component 4 in the loading process, and the loading stiffness is k at the momentl. When the external force is reduced and the transmission shaft 3 moves before stopping, the segment BC represents that the static friction force is reduced along with the reduction of the external force and reaches the reverse maximum value when reaching the point C. The CDO segment is represented inThe process of overcoming friction and recovering the original position under the action of the resilience force of the spring 5, wherein the rigidity of the shock absorber 11 is the unloading rigidity ku. Under the reciprocating action, the hysteresis curves of the spring 5 and the friction component 4 are in a symmetrical double-flag shape of one quadrant and three quadrants.
The force analysis of the friction assembly 4 is described by taking a second middle combination form as an example, and the first combination form, i.e. a special case that the number of pairs of the inner ring and the outer ring of the second combination form is 1. The friction member disposed at the lower end of the shock absorber 11 was taken out, and the isolated body thereof was subjected to a stress analysis as shown in FIG. 9. The numbers of the inner ring are 0, 1 and 2 … n-1 from bottom to top in sequence, and the numbers of the outer ring are 1 and 2 … n from bottom to top in sequence.
The significance of each parameter in the stress analysis discussion is as follows:
F0-0 inner ring force;
fithe friction force between the conical surfaces of the No. i inner ring and the adjacent outer ring;
Nipositive pressure between the conical surfaces of the No. i inner ring and the adjacent outer ring;
fi w-friction between the outer ring and the inner wall of the device;
Figure BDA0003017874360000101
-positive pressure between the outer ring # i and the inner wall of the device;
Fi-thrust of the end face between the inner and outer rings No. i;
Fn-spring return force;
theta-inner and outer ring cone angles;
n is the number of inner and outer rings;
μ1-the coefficient of friction between the inner and outer rings;
μ2-coefficient of friction between the outer ring and the inner wall of the device.
The calculation assumes:
1) the effect of acceleration is negligible compared to friction and thus a static equilibrium condition can be adopted.
2) The difference between the coefficient of sliding friction and the coefficient of static friction was ignored.
3) The friction force between the inner ring of the friction assembly and the end faces of the transmission shaft and the inner ring and the outer ring can be ignored.
When the friction assembly moves upwards from the initial position, the vertical stress balance of the No. 0 inner ring is as follows:
F0＝N0 sinθ+f0cosθ (1)
F0friction force between No. 0 inner ring and adjacent outer ring conical surface;
will f is0＝μ1N0And finishing by substituting the formula:
Figure BDA0003017874360000111
the balance of the horizontal and vertical directions of the No. 1 outer ring is as follows:
Figure BDA0003017874360000112
will f is0＝μ1N0，
Figure BDA0003017874360000113
And finishing by substituting the formula:
F1＝(sinθ+μ1 cosθ+μ1μ2 sinθ-μ2 cosθ)N0 (4)
F1is the end face thrust between the No. 1 inner ring and the No. 1 outer ring; n is a radical of0The positive pressure between the conical surfaces of the No. 0 inner ring and the adjacent outer ring;
the same analysis is performed for the remaining inner and outer rings, and the following recursion equation can be obtained:
Figure BDA0003017874360000114
from formula (5):
Figure BDA0003017874360000115
from equation (6), the relationship between the spring and friction assembly force and the spring return force is:
Figure BDA0003017874360000116
F0inner ring output of No. 0; fnThe resilience force of the spring is adopted;
because Fn＝ksx, wherein ksFor spring rate, x is the amount of spring compression, so there are:
Figure BDA0003017874360000117
if the deformation of the transmission shaft is neglected, that is, the conversion stiffness is considered to be much larger than the loading stiffness, the spring deformation x is the relative displacement of the two ends of the shock absorber 11, so that the calculation expression of the loading stiffness of the shock absorber 11 is obtained:
Figure BDA0003017874360000121
klloading the shock absorber 11 with stiffness;
when unloaded, as in FIG. 9
Figure BDA0003017874360000122
Reverse direction, so only mu needs to be added2＝-μ2The calculation expression of the unloading rigidity of the shock absorber 11 can be obtained by substituting formula (9):
Figure BDA0003017874360000123
kuunloading stiffness for shock absorber 11; mu.s1Is the friction coefficient between the inner and outer rings; mu.s2The coefficient of friction between the outer ring and the inner wall of the device;
the third combination form and the fourth combination form both adopt a double-conical-surface friction assembly, the fourth combination form is taken as an example to perform stress analysis, the third combination form, namely the fourth combination form takes a special example that the number of inner rings is 1, and the stress analysis of the isolated body is shown in fig. 10. The numbers of the inner rings are 0, 1 and 2 … n from bottom to top in sequence, and the numbers of the outer rings are 1 and 2 … n from bottom to top in sequence.
Here F0As a counter-force of a spring, FnTo exert a force on the shock absorber 11.
When the friction assembly moves downwards from the initial position, the vertical stress balance of the No. 0 inner ring is as follows:
F0＝N0 sinθ+f0cosθ (1)
will f is0＝μ1N0And finishing by substituting the formula:
Figure BDA0003017874360000124
the balance of the horizontal and vertical directions of the No. 1 outer ring is as follows:
Figure BDA0003017874360000125
will f is0＝μ1N0、f1＝μ1N1、
Figure BDA0003017874360000126
Substituting the formula into the formula to obtain the product:
Figure BDA0003017874360000127
the formula is solved as follows:
Figure BDA0003017874360000128
where a and b are constants determined by two friction coefficients and inner and outer ring taper angles in the damper 11:
Figure BDA0003017874360000131
the same analysis of the remaining outer rings gives the following recurrence equation:
Figure BDA0003017874360000132
is composed of
Figure BDA0003017874360000133
The total friction force of all the outer rings at the upper end of the shock absorber 11 can be obtained:
Figure BDA0003017874360000134
substituting formula (1) into formula (8) to obtain:
Figure BDA0003017874360000135
order:
Figure BDA0003017874360000136
the vertical static balance of the friction assembly 4 is considered as a whole, and the method comprises the following steps:
Fn＝f+F0＝(1+β)F0 (11)
because F0＝ksx, so there are:
Fn＝(1+β)ksx (12)
if the deformation of the transmission shaft is ignored, the calculation expression of the loading rigidity of the shock absorber 11 is as follows:
Figure BDA0003017874360000137
when unloading, the friction force between the outer ring and the cylinder wall is opposite, so that the calculation expression of the unloading rigidity of the shock absorber 11 can be obtained by only replacing mu 2 with-mu 2 into formula (13):
Figure BDA0003017874360000138
as can be seen from the structural principle of the present shock absorber 11, the line segment AB in the loading process in fig. 8 is extended in the reverse direction and intersects the horizontal axis at point E, which is the virtual free length state of the spring without being pressed. When the actual shock absorber 11 triggers power to design, can regard the power value of dotted line EA section and the nodical power of axis of ordinates as the required drive power of trigger friction subassembly approximately, then AB section linear equation can write:
F＝kld+Fs0+fl (15)
wherein F is the friction member output force, d is the friction member displacement, Fs0Initial pre-stress of the spring, flIs the friction force when the friction component is triggered to start. Let l0For the initial precompression of the spring, Fs0＝ksl0. The line AB intersects the horizontal axis at point E, where F is 0 and d is-l0When the displacement of the friction component in the static state is approximately zero when the friction component is triggered and started, the driving force required for triggering the friction component is the sum of the initial pre-pressure and the initial friction force of the spring, namely Fs0+flThe design value may be taken as kll0。
Similarly, the unloading process CD segment is extended to intersect the horizontal axis at point E, which is also the virtual free length state where the spring is not compressed. The CD segment line equation can be written as:
F＝kud+Fs0-fu (16)
in the formula (f)uThe friction force when the friction assembly is unloaded and restored to the full reset is approximately considered to be the difference between the initial pre-pressure of the spring and the friction force when the friction assembly is unloaded and restored. The CD line intersects the horizontal axis at point E, where F is 0 and d is-l0Obtaining a restoring force Fs0-fuMay be taken as kul0。
The working effect of the viscoelastic element is analyzed, and the output force of the viscoelastic element is as follows:
Figure BDA0003017874360000141
wherein f is the viscoelastic element force;
k' -storage stiffness;
u-viscoelastic element displacement;
Figure BDA0003017874360000142
-viscoelastic element speed;
eta-loss factor;
ω -excitation frequency.
When the viscoelastic element is acted by simple harmonic force, the viscoelastic element is displaced to u-u0sin ω t, then the velocity is
Figure BDA0003017874360000143
From formula (17):
Figure BDA0003017874360000144
according to cos2ωt+sin2ω t is 1 available:
Figure BDA0003017874360000145
the force vs. displacement hysteresis relationship of the viscoelastic element is shown in fig. 11. U in the figure0Denotes the maximum displacement, f ' is the damping force corresponding to the maximum displacement, k ' ═ f '/u0F "is the damping force when the displacement is zero, f ═ η k' u0。
The damper 11 fully utilizes the hysteresis superposition gain effect of the friction component and the viscoelastic element in the first quadrant and the third quadrant, the larger the displacement of the damper 11 is, the larger the friction force of the friction component is, the more energy is consumed, the larger the speed of the damper 11 is, the larger the damping force of the viscoelastic element is, and the stronger the energy consumption effect is. Therefore, the present damper 11 can suppress the earthquake reaction of the protected electric equipment 12 from both the displacement and the velocity. The shock absorber 11 is a self-restoring shock absorber 11, and in the process of restoring the internal elements of the shock absorber 11, such as the CD section in fig. 8, if the restoring speed is too fast under the action of an earthquake, the damping force of the viscoelastic element in the second quadrant and the fourth quadrant in fig. 11 can control the device not to be collided with the original position too fast to generate impact.
The electrical equipment 12 itself has a certain anti-seismic property, and when designing the shock absorber 11, the initial pre-pressure F of the spring required when the shock absorber 11 is triggered should be considereds0Friction force f of friction assemblylAnd f' of the viscoelastic element as the trigger force of the shock absorber 11, the trigger force is set to avoid the misoperation of the electrical equipment 12 in the strong wind or normal mechanical operation process, and when an earthquake exceeding the shock resistance of the equipment, the shock absorber 11 can be triggered to work so as to protect the electrical equipment 12. In addition, the restoring force F of the friction component should be considered after the earthquake disappears and if the equipment has certain inclinations0-fuThe restoring force should be sufficient to overcome the overturning force caused by f ″ during the recovery of the viscoelastic element and the tilting of the device after the shock, so as to ensure that the shock absorbing device and the electrical device 12 can be successfully restored after the shock.
The main flow of the damping device design is as follows: firstly, the distribution and the quantity of the shock absorbers 11 are preliminarily determined according to the number and the positions of the flange bolt holes at the bottom of the pillar type electrical equipment 12 and the size of the bottom flange. And secondly, calculating the trigger force of the shock absorber 11 according to the earthquake fortification requirement of the equipment and the equipment parameters. Selecting the form and the spring type of the friction assembly according to the seismic fortification requirement of the electrical equipment 12 and the design trigger force of the shock absorber 11, and determining the cone angle theta and the spring stiffness k of the inner ring and the outer ring of the friction assemblysAnd initial precompression l0Parameters such as the loss factor eta and the storage rigidity k' of the viscoelastic element. Checking the damping effect of the damping scheme on the equipment, checking whether the maximum stroke of the damping device is within the designed stroke range, and checking whether the restoring force of the damping device is enough to overcome the overturning force borne by the device so as to reset the electrical equipment 12. If the checking result meets the design requirementIf so, the design of the damping device is finished; otherwise, returning to the first step to restart, and adjusting the design until the checking calculation is passed.
1. This damping device can rationally set up the trigger force of device, guarantees that electrical equipment 12 can not the malfunction under exogenic action such as strong wind, mechanical operation, and when the earthquake that surpasss equipment shock resistance itself takes place, the device just is triggered work, protection electrical equipment 12 safety and stability operation.
2. The friction component and the viscoelastic element in the damping device provide two energy consumption mechanisms, and can respectively play a remarkable damping effect on the conditions of large swing amplitude and high speed of the electrical equipment 12. When the equipment is separated from the original position and the swing amplitude is increased, the two damping elements act together in one quadrant and three quadrants in the force-displacement relation, and in the return process of the equipment, the damping forces of the elastic elements in the two quadrants and the four quadrants in the force-displacement relation can control the equipment not to be collided back to the original position too fast to generate impact under the resilience force of the spring and the action of an earthquake.
3. The post-earthquake damping device can realize self-recovery, the electrical equipment 12 can return to the initial position after each earthquake, and adverse effects such as inclination and migration cannot be accumulated after multiple earthquakes and aftershocks.
4. The invention provides a definite design calculation method to realize the functions.
Example 3:
the invention based on the same inventive concept also provides a damping device design method, which comprises the following steps:
determining the position and number of the shock absorbers 11 based on the parameters of the electrical equipment 12 provided on the support mechanism 10;
determining a design trigger force for each shock absorber 11 based on the parameters and seismic fortification requirements of said electrical equipment 12 and the location and number of said shock absorbers 11;
determining the type of shock absorber 11 from the design trigger force of said shock absorber 11;
wherein, the type of the shock absorber 11 is determined by the energy dissipation element adopted by the shock absorber 11 and the elastic member adapted to the energy dissipation element; the design triggering force is determined by the force generated by the damper 11 drive shaft 3 which in turn passes through the housing and the elastic member to move the dissipative element located inside the housing of the damper 11 in the earthquake.
Preferably, the energy consumption element includes: a damping member and/or a friction assembly.
Preferably, the shock absorbers are of the type comprising:
when the energy dissipation element is a damping part, the damping part and the generating and elastic part form a shock absorber;
when the dissipative element is the friction component 4, the damper is composed of the friction component 4 and an elastic member determined by the relation between the spring reaction force and the friction component 4;
when the dissipative element is a damping member and a friction member 4, the damper is composed of the friction member 4, the damping member and an elastic member determined by the relationship between the spring reaction force and the friction member 4.
Preferably, the design trigger force is determined by the force generated by the transmission shaft 3 of the shock absorber 11 passing through the housing and the elastic member in sequence to drive the dissipative element inside the housing of the shock absorber 11 in an earthquake, and comprises:
when the shock absorber is of the type formed by the damping part and the elastic part, the design trigger force is determined by the output force generated by the movement of the viscoelastic element of the damping part driven by the transmission shaft 3 relative to the transmission shaft 3 in the earthquake;
when the shock absorber is of the type consisting of said friction assembly 4 and an elastic member determined by the relationship of the spring reaction force to said friction assembly 4, the triggering force is designed to be the force with which the drive shaft 3 drives the outer ring 8 of the friction assembly 4 in different combinations in the earthquake to move relative to the housing;
when the shock absorber is of the type consisting of said friction assembly 4, a damping member and an elastic member defined by the relationship between the spring reaction and said friction assembly 4, the design triggering force is determined by the combined forces generated by the movement of the viscoelastic element of the damping member relative to the drive shaft 3 during an earthquake by the drive shaft 3 and the movement of the outer ring 8 of the friction assembly 4 relative to the housing in different combinations.
Preferably, the force with which the outer ring 8 of the friction assembly 4 moves relative to the housing in said different combinations is obtained by multiplying the loading stiffness of the shock absorber by the precompression of the elastic member.
Preferably, the friction assembly 4 comprises, in combination:
a first combination form composed of a pair of single-cone inner rings 9 and an outer ring 8;
a second combination form formed by overlapping a plurality of pairs of single conical surface inner rings 9 and outer rings 8;
a third combination form consisting of two single-conical inner rings 9 and a double-conical outer ring 8;
or a fourth combination form consisting of two single-conical-surface inner rings at two ends, n double-conical-surface inner rings in the middle and n +1 groups of double-conical-surface outer rings.
Preferably, the loading stiffness and the unloading stiffness when the friction pack 4 is in the first combination and the second combination are calculated as follows:
Figure BDA0003017874360000171
in the formula, klThe loading stiffness of the shock absorber; theta is the taper angles of the inner ring and the outer ring; k is a radical ofsIs the spring rate; mu.s1: the friction coefficient between the inner ring and the outer ring; mu.s2: coefficient of friction between the outer ring and the housing; n is the number of inner rings and outer rings;
Figure BDA0003017874360000172
in the formula, kuIs the unload stiffness of the shock absorber.
Preferably, the loading stiffness and the unloading stiffness when the friction pack (4) is in the third combination and the fourth combination are calculated as follows:
Figure BDA0003017874360000173
in the formula, klThe loading stiffness of the shock absorber; theta is the taper angles of the inner ring and the outer ring; k is a radical ofsIs the spring rate; mu.s1: the friction coefficient between the inner ring and the outer ring; mu.s2: coefficient of friction between the outer ring and the housing; n is the number of inner rings and outer rings;
Figure BDA0003017874360000181
in the formula, kuIs the unload stiffness of the shock absorber.
Preferably, the damping member output force is calculated according to the following formula:
Figure BDA0003017874360000182
in the formula, f: a viscoelastic element force; k': storing the stiffness; u: displacement of the viscoelastic element;
Figure BDA0003017874360000183
a viscoelastic element speed; eta: a loss factor; and omega represents the excitation frequency.
The two energy dissipation elements of the damping device can be used independently. When the damping piece is adopted as the energy dissipation element alone, the device is shown in fig. 12, at the moment, no friction component exists, the mechanical property of the spring-friction component in the original design method is changed into the mechanical property of an individual compression spring, the force-displacement curve is shown in fig. 13, and when the design is carried out, k isl＝ku＝ksAnd f islAnd fuAre all 0. When the friction component is adopted as the energy dissipation element alone, the device is as shown in fig. 14, and no damping member is provided, so that the design only needs to consider the mechanical property of the spring-friction component, and f is 0.
As will be appreciated by one skilled in the art, embodiments of the present application may be provided as a method, system, or computer program product. Accordingly, the present application may take the form of an entirely hardware embodiment, an entirely software embodiment or an embodiment combining software and hardware aspects. Furthermore, the present application may take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, and the like) having computer-usable program code embodied therein.
The present application is described with reference to flowchart illustrations and/or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the application. It will be understood that each flow and/or block of the flow diagrams and/or block diagrams, and combinations of flows and/or blocks in the flow diagrams and/or block diagrams, can be implemented by computer program instructions. These computer program instructions may be provided to a processor of a general purpose computer, special purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, create means for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be stored in a computer-readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer-readable memory produce an article of manufacture including instruction means which implement the function specified in the flowchart flow or flows and/or block diagram block or blocks.
These computer program instructions may also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions which execute on the computer or other programmable apparatus provide steps for implementing the functions specified in the flowchart flow or flows and/or block diagram block or blocks.
The present invention is not limited to the above embodiments, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention are included in the scope of the claims of the present invention which are filed as the application.

Claims (11)

1. A shock-absorbing device, characterized by comprising a support mechanism (10) and a plurality of shock absorbers (11);
the shock absorber (11) comprises a shell, an energy dissipation element, an elastic piece and a transmission shaft (3) which sequentially penetrates through the shell and the elastic piece, wherein the energy dissipation element and the elastic piece are positioned in the shell;
the housing includes: an outer cylinder (1) and two end covers (2);
two ends of the outer cylinder (1) are respectively connected with the end covers (2);
the energy dissipation elements are arranged on the inner sides of the two end covers (2);
the supporting mechanism (10) is arranged in the middle of the bottom of the electrical equipment (12), and the plurality of shock absorbers (11) are fixed on the electrical equipment (12) through the transmission shaft (3);
the elastic part comprises a spring (5) and a sliding plate, and the middle part of the sliding plate is provided with a hole for the transmission shaft (3) to pass through;
the sliding plates are arranged at two ends of the spring (5);
the energy dissipating element comprises: a friction assembly (4) and a damping member;
the transmission shaft (3) penetrates through the friction assembly (4) and the damping piece;
the damping member includes: a damping cylinder (7), a viscoelastic element (6) and a strut inside the damping cylinder (7);
one end of the strut is connected with the damping cylinder (7), and the other end of the strut is connected with the end cover (2);
the viscoelastic element (6) has a height smaller than the height of the damping cylinder (7);
the height of the damping cylinder (7) is smaller than that of the spring when the spring is compressed to the maximum;
the damping cylinder (7) is limited and fixed by the support, the transmission shaft (3) moves up and down, dislocation continuously occurs on the inner side and the outer side of the viscoelastic element (6), damping is generated through shear deformation of the viscoelastic element (6), and seismic energy is consumed.
2. A shock absorbing device as claimed in claim 1, wherein said friction assembly (4) comprises: a multi-segment outer ring segment and an inner ring (9);
the multiple sections of outer ring sections are sequentially connected to form an outer ring (8); the inner ring (9) is a circular ring with an external conical surface;
the inner conical surface of the outer ring (8) is attached to the outer conical surface of the inner ring (9).
3. A shock absorbing device as claimed in claim 2, wherein the combined form of said outer ring (8) and inner ring (9) comprises: a first combination of a single-cone inner ring (9) and a single-cone outer ring (8);
a second combination form formed by overlapping a plurality of inner rings (9) with single conical surfaces and a plurality of outer rings (8) with single conical surfaces;
a third combination form consisting of two inner rings (9) with single conical surfaces and an outer ring (8) with double conical surfaces;
or a fourth combination form consisting of two inner rings (9) with single conical surfaces at two ends, n inner rings (9) with double conical surfaces in the middle and n +1 outer rings (8) with double conical surfaces.
4. A shock-absorbing device as claimed in claim 3, wherein the upper and lower end faces of the inner ring (9) each have an outer diameter greater than the outer diameter of the damping cylinder (7) and have holes for the passage of the strut, and the slide plate also has holes for the passage of the strut.
5. The shock absorbing device of claim 1, further comprising: a collar;
the collar is arranged on the upper part of the transmission shaft (3), the lower end surface of the collar is contacted with the friction component (4), and the upper end surface of the collar is contacted with the flange of the electric equipment (12).
6. A method of designing a shock absorbing device, comprising:
determining the position and number of the shock absorbers (11) on the basis of the parameters of the electrical equipment (12) arranged on the support mechanism (10);
determining a design trigger force for each of said shock absorbers (11) based on parameters and seismic fortification requirements of said electrical equipment (12) and the location and number of said shock absorbers (11);
determining the type of the shock absorber (11) from the design trigger force of the shock absorber (11);
wherein the type of the shock absorber (11) is determined by the energy dissipation element adopted by the shock absorber (11) and the elastic member matched with the energy dissipation element; the design trigger force is determined by the force generated by a transmission shaft (3) of the shock absorber (11) which sequentially penetrates through the shell and the elastic piece and drives the dissipative element positioned inside the shell of the shock absorber (11) to move in an earthquake;
the dissipative element, comprising: a damping member and/or a friction assembly;
the types of the shock absorber include:
when the energy dissipation element is a damping piece, the shock absorber (11) is formed by the damping piece and an elastic piece;
when the dissipative element is a friction component (4), the damper is composed of the friction component (4) and an elastic component determined by the relation between the spring reaction force and the friction component (4);
when the dissipative element is a damping piece and a friction component (4), the damper is composed of the friction component (4), the damping piece and an elastic piece determined by the relation between the spring reaction force and the friction component (4);
the design trigger force is determined by the force generated by the damper (11) transmission shaft (3) sequentially passing through the shell and the elastic piece to drive the energy dissipation element positioned in the shell of the damper (11) to move in an earthquake, and comprises the following steps:
when the shock absorber is of the type consisting of the damping member and the elastic member, the design trigger force is determined by the output force generated by the movement of the viscoelastic element (6) of the damping member in the earthquake of the transmission shaft (3) relative to the transmission shaft (3);
when the shock absorber is of the type consisting of said friction assembly (4) and an elastic member determined by the relationship of the spring reaction force to said friction assembly (4), the design triggering force is determined by the force of the drive shaft (3) in an earthquake driving the outer ring (8) of the friction assembly (4) in different combinations in relation to the housing;
when the shock absorber is of the type consisting of the friction assembly (4), a damping member and an elastic member determined by the relationship between the spring reaction and the friction assembly (4), the design triggering force is determined by the force generated by the movement of the viscoelastic element (6) of the damping member relative to the transmission shaft (3) in an earthquake of the transmission shaft (3) and the force generated by the movement of the outer ring (8) of the friction assembly (4) relative to the housing in different combinations.
7. A design method of a shock-absorbing device according to claim 6, characterized in that the force of the outer ring (8) of the friction pack (4) in different combinations moving relative to the housing is obtained by multiplying the loading stiffness of the shock absorber by the precompression of the elastic member.
8. The method for designing a shock-absorbing device as set forth in claim 7, wherein the combined form of said friction members (4) comprises:
a first combination of a single-cone inner ring (9) and a single-cone outer ring (8);
a second combination form formed by overlapping a plurality of inner rings (9) with single conical surfaces and a plurality of outer rings (8) with single conical surfaces;
a third combination form consisting of two inner rings (9) with single conical surfaces and an outer ring (8) with double conical surfaces;
or a fourth combination form consisting of two inner rings (9) with single conical surfaces at two ends, n inner rings (9) with double conical surfaces in the middle and n +1 outer rings (8) with double conical surfaces.
9. The designing method of a damper device according to claim 8, wherein the loading rigidity and the unloading rigidity when the friction member (4) is in the first combination and the second combination are calculated as follows:
Figure FDA0003498360240000031
in the formula, klThe loading stiffness of the shock absorber; theta is the taper angles of the inner ring and the outer ring; k is a radical ofsIs the spring rate;μ1: the friction coefficient between the inner ring and the outer ring; mu.s2: coefficient of friction between the outer ring and the housing; n is the number of inner rings and outer rings;
Figure FDA0003498360240000041
in the formula, kuIs the unload stiffness of the shock absorber.
10. The designing method of a damper device according to claim 8, wherein the loading rigidity and the unloading rigidity when the friction member (4) is in the third combination and the fourth combination are calculated as follows:
Figure FDA0003498360240000042
in the formula, klThe loading stiffness of the shock absorber; theta is the taper angles of the inner ring and the outer ring; k is a radical ofsIs the spring rate; mu.s1: the friction coefficient between the inner ring and the outer ring; mu.s2: coefficient of friction between the outer ring and the housing; n is the number of inner rings and outer rings;
Figure FDA0003498360240000043
in the formula, kuIs the unload stiffness of the shock absorber.
11. The method of claim 6, wherein the force exerted by the viscoelastic element is calculated as follows:
Figure FDA0003498360240000044
in the formula, f: the force of the viscoelastic element; k': storing the stiffness; u: displacement of the viscoelastic element;
Figure FDA0003498360240000045
a viscoelastic element speed; eta: a loss factor; and omega represents the excitation frequency.
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