CN114934972B - Damping-containing nonlinear spring limiter for power plant boiler steel frame structure - Google Patents
Damping-containing nonlinear spring limiter for power plant boiler steel frame structure Download PDFInfo
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- CN114934972B CN114934972B CN202210651951.XA CN202210651951A CN114934972B CN 114934972 B CN114934972 B CN 114934972B CN 202210651951 A CN202210651951 A CN 202210651951A CN 114934972 B CN114934972 B CN 114934972B
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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
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/002—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion characterised by the control method or circuitry
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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
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
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Abstract
The invention provides a damping-containing nonlinear spring limiter for a steel frame structure of a power plant boiler, which comprises a steel cable, a linear damper and a steel block, wherein the steel cable is connected with the linear damper; two ends of the steel cable are connected to the cross beams on the two sides of the supporting frame and are horizontally arranged on the front side or the rear side of the furnace body at intervals; the linear damper is vertical to the surface of the furnace body and is connected between the steel cable and a cross beam on the front side or the rear side of the support frame; the steel block is connected to one side of the furnace body, which is adjacent to the steel cable, and the position of the steel block corresponds to the linear damper. The damping-containing nonlinear spring limiter for the steel frame structure of the power plant boiler can reduce the force conducted by the boiler body to the supporting structure when the boiler body generates small vibration, and can also effectively absorb energy through damping, thereby improving the vibration of the whole structure. Meanwhile, when the furnace body generates large displacement, the limiting stopper can provide larger counter force than the linear spring, so that the furnace body is prevented from colliding with the supporting structure, and the limiting effect is better played.
Description
Technical Field
The invention relates to the field of nonlinear spring limiters, in particular to a damping-containing nonlinear spring limiter for a power plant boiler steel frame structure.
Background
As an important component of a lifeline project, power resources play a great role, and coal power occupies a large proportion in the power resources, so that the anti-seismic research on coal power generation equipment and boiler steel frame structures is necessary. The boiler steel frame structure is a special suspension type structure and mainly comprises a boiler body and a supporting structure. The current research discovers that the limiter connecting the furnace body and the supporting structure obviously influences the anti-seismic effect of the whole structure. The stopper widely adopted at present is often simple in form and poor in effect, and the most representative stopper is used for cutting off the steel beam. The stopper is a linear spring in an elastic stage, consumes energy conducted by earthquake through plastic deformation, and mainly has the following defects: 1) The vibration of the furnace body is not only caused by earthquake, but also small vibration (compared with earthquake) of the furnace body can be caused by wind load, and the linear spring can also generate large load on the supporting system when the furnace body vibrates in small amplitude; 2) The limiter does not have reusability due to energy consumption of plastic deformation, and the furnace body can swing back and forth in one earthquake, which means that after the limiter is invalid, no buffer device is arranged between the furnace body and the supporting structure any more, and the supporting structure can be rapidly damaged due to violent impact. Therefore, it is necessary to provide a specific limiting device for the boiler and the steel frame system.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides the damping-containing nonlinear spring limiter for the steel frame structure of the power plant boiler, which not only can reduce the force transmitted to the supporting structure by the boiler body when the boiler body generates small vibration, but also can effectively absorb energy through damping, thereby improving the vibration of the whole structure. Meanwhile, when the furnace body generates large displacement, the limiting stopper can provide larger counter force than the linear spring, so that the furnace body is prevented from colliding with the supporting structure, and the limiting effect is better played.
In order to achieve the purpose, the invention provides a damping-containing nonlinear spring limiter for a steel frame structure of a power plant boiler, which comprises a steel cable, a linear damper and a steel block, wherein the steel cable is connected with the linear damper; the boiler steel frame structure comprises a boiler body and a supporting frame, wherein the boiler body is suspended in the supporting frame, and the periphery of the supporting frame is provided with a beam at the same height; two ends of the steel cable are connected to the cross beams on two sides of the supporting frame and are horizontally arranged on the front side or the rear side of the furnace body at intervals; the linear damper is perpendicular to the surface of the furnace body and is connected between the steel cable and one cross beam on the front side or the rear side of the support frame; the steel block is connected to one side of the furnace body, which is close to the steel cable, and the position of the steel block corresponds to that of the linear damper.
Preferably, the linear damper satisfies the formula:
wherein D is any real or negative number; c represents the damping of the linear damper; t represents the tension of the steel cable, and m represents the mass per unit length of the steel cable;
the optimal linear damper damping is achieved at D → -infinity, at which time
C at this time is critical damping when the free vibration is most rapidly attenuated.
Due to the adoption of the technical scheme, the invention has the following beneficial effects:
the invention can reduce the force transmitted to the supporting structure by the furnace body when the furnace body generates small vibration by matching the steel cable, the linear damper and the steel block, and can also effectively absorb energy by damping, thereby improving the vibration of the whole structure. Meanwhile, when the furnace body generates large displacement, the limiter can provide larger counterforce than the linear spring, so that the furnace body is prevented from colliding with the supporting structure, and the limiting effect is better played. Through the parameter setting of the linear damper, the vibration of the limiter can be reduced to the maximum extent.
Drawings
FIG. 1 is a front view of a damped non-linear spring retainer for a power plant boiler steel frame structure in an embodiment of the present invention;
FIG. 2 is a top view of a damped non-linear spring retainer for a power plant boiler steel frame structure in accordance with an embodiment of the present invention;
FIG. 3 is a first schematic model of an embodiment of the present invention;
FIG. 4 is a diagram of a second mathematical model according to an embodiment of the present invention;
FIG. 5 is a third mechanical model of an embodiment of the present invention;
FIG. 6 is a schematic view of a steel cable static mechanical model according to an embodiment of the present invention;
FIG. 7 is a schematic diagram of a single degree of freedom model of the buffer performance of a limiter according to an embodiment of the present invention;
FIG. 8 is a graph of the displacement time course of a main structure when a damping non-linear spring retainer for a steel frame structure of a power plant boiler according to the present invention is installed;
FIG. 9 is a graph of the time course of the displacement of the main structure without the installation of the stopper according to the embodiment of the present invention;
FIG. 10 is a graph of the displacement time course of the main structure when only the steel cable is installed according to the embodiment of the present invention;
FIG. 11 is a graph of the displacement time course of the main structure when only the damper is installed according to the embodiment of the present invention;
fig. 12 is a graph of the displacement time course of the main structure when the linear spring and the damper are installed according to the embodiment of the invention.
Detailed Description
The following description of the preferred embodiments of the present invention will be provided in conjunction with the accompanying drawings, which are set forth in the accompanying drawings and figures 1-12, to provide a better understanding of the function and features of the invention.
Referring to fig. 1 to 12, a damping-containing nonlinear spring retainer for a steel frame structure of a power plant boiler according to an embodiment of the present invention includes a steel cable 1, a linear damper 2, and a steel block 3; the boiler steel frame structure comprises a boiler body and a supporting frame, wherein the boiler body is suspended in the supporting frame, and the peripheries of the supporting frame are respectively provided with a beam at the same height; two ends of the steel cable 1 are connected to the cross beams on two sides of the supporting frame and are horizontally arranged on the front side or the rear side of the furnace body at intervals; the linear damper 2 is vertical to the surface of the furnace body and is connected between the steel cable 1 and a beam on the front side or the rear side of the support frame; the steel block 3 is connected to one side of the furnace body, which is adjacent to the steel cable 1, and the position of the steel block corresponds to that of the linear damper 2.
Preferably, the linear damper 2 satisfies the formula:
wherein D is any real or negative number; c represents the damping of the linear damper 2; t represents the tension of the wire rope 1, and m represents the mass per unit length of the wire rope;
the optimal linear damper 2 damping is achieved at D → -infinity, at which time
C at this time is the critical damping at which the free vibration decays most rapidly.
The damping-containing nonlinear spring limiter for the steel frame structure of the power plant boiler has the following parameter derivation processes:
referring to fig. 2 to 4, due to the existence of the steel block 3, only concentrated load is generated when the furnace body contacts the steel cable 1. Since the static analysis is performed when the rigidity of the stopper is deduced, the damping does not act, and therefore, the damper can be removed in the analysis process. Only the effect of the stopper in the elastic range is considered, so the whole analysis process is divided into two parts, the first part is the analysis in the x-y plane and the second part is the analysis in the x-z plane. The analysis of the x-y plane is the state of the steel cable 1 under the self weight, the analysis of the x-z plane is the state of the concentrated load of the steel cable 1 in the midspan, and the superposition of the two is the state of the lateral midspan stress of the stopper. The x-y plane analysis has been studied, and is not repeated, and the x-z plane analysis is mainly performed. And (3) taking the F action point as a demarcation point, dividing the steel cable 1 into a left part and a right part, respectively carrying out stress analysis on the two parts, and establishing a mechanical equation. The analysis on the left side is performed first. According to the stress balance, the following results are obtained:
wherein H is the horizontal restraining force at the end point, V is the vertical restraining force at the end point, L 0 The length of the steel cable 1 in a relaxed state, l is the span of the steel cable, E is the tensile elastic modulus of the steel cable, A is the sectional area of the steel cable, p is the linear distance from the original point to the (x, z) point, s is the Lagrange coordinate system coordinate fixed on the steel cable 1, and the value range is [0 0 ]. Solving the system of equations can yield T 2 X, z as a function of s.
The analysis on the right is performed below and is based on force balance:
can obtain T in the same way 2 X, z with respect to s, taking into account the continuity of the actual cable 1, and therefore
Thus, it is possible to obtain:
wherein z(s) is a target calculation function, and the z(s) can obtain the displacement of the steel cable 1 in the midspan position caused by the F, i.e. the carry-in
And (4) finishing. Boundary conditions are then substituted to find the expression for H and V. At the right endpoint, there are
Wherein l is the span of the steel cable, and Eq. (4) is taken in, and then:
bringing the result into z(s) and letting
Namely, when the steel cable 1 is subjected to concentrated force F in midspan, the midspan displacement is as follows:
where H is solved by the second expression in eq. (5), this expression derivation process does not use small deformation assumptions and is therefore applicable to large deformations. Obviously, this expression is too complex to be used in subsequent kinetic analysis, requiring simplification. The method adopted by the method is curve fitting, namely after determining each parameter, substituting different F, solving to obtain H, calculating the corresponding delta, and obtaining an F-delta curve, so that a fitting expression can be obtained, and a cubic polynomial can be basically fitted without errors.
After the F- δ relationship of the steel cable 1 is obtained, a proper damper damping is required to be selected, so that the stopper can stop vibrating rapidly when being excited by an external load, and the critical damping can certainly meet the requirement, so that free vibration analysis is performed on the steel cable 1 to find an expression of the critical damping. Since the stopper is laterally stressed during operation, the initial configuration is not changed by its own weight, and the wire rope 1 can be regarded as a tensioned string. The damper is located at the mid-span point. The analysis chart is shown in fig. 5:
damping divides the steel cable 1 into two parts, left and right, for each of which the displacement caused by the lateral free vibration is considered to be a small displacement, so that the tension caused by the vibration is negligible, and since the vibration plane is perpendicular to the direction of the action of gravity, the action of gravity is not considered, while the anti-lateral stiffness and the structural damping of the steel cable 1 are ignored, so that the free vibration equation can be written as:
wherein w k For lateral displacement of the cable, x k Is the longitudinal coordinate of the wire rope 1 of the kth part, m is the unit length mass of the wire rope, and T is the wire rope tension. Eq. (7) is always true except for the damper installation position where the displacement is continuous and the force is balanced. To solve eq. (7), a time parameter τ = ω is introduced 01 t wherein
Assume that the solution of Eq. (7) is:
w k (x k ,τ)＝W k (x k )e λτ #Eq.(8)
where λ is a dimensionless complex eigenvalue, substituting eq. (8) into eq. (7) yields:
the solution of eq. (9) is of complex vibration type corresponding to λ, and in order to have continuity of the solution at the damping installation, the solution can be written as:
where γ is the amplitude of the mode shape at the damper, and its value cannot be determined nor required. After the continuity is satisfied, the mechanical balance needs to be satisfied, so the equation can be obtained:
bringing eq. (8) and eq. (10) into eq. (11) is available:
obviously, λ can be written in the form of λ = D + Bi, where i is an imaginary unit, and eq. (12) can be expanded in terms of real and imaginary parts, and the equation holds when both the real and imaginary parts are 0:
2sin(πB)cosh(πD)＝sin(2πB)#Eq.(13a)
and Eq. (13 a) is an equation with an imaginary part of 0, and Eq. (13 b) is an equation with a real part of 0. Due to the fact that
In practical engineering, D is always positive, and D is always negative, so that only the case that D is less than 0 is considered in practical significance. Eq. (8) shows that when λ is a purely real number, i.e., D, free vibration is exponentially damped to an equilibrium position without fluctuation, and the vibrationThe situation is consistent with the vibration situation desired herein, so the finding of c is followed. When B =0, eq. (13 a) is automatically established, and therefore is not considered, only eq. (13B) is considered. Eq. (13 a) can be simplified as:
the left side of the equation is meaningful for positive numbers at D ∈ (— ∞, 0), while it can be observed that when D → - ∞, the left side → 2, at which time
I.e. the critical damping when the free vibration decays fastest.
The cable tension T is obtained next. When the steel cable 1 is in a static state, the tension is caused only by gravity and pretension (or by the pretension), so that an analysis image can be obtained as shown in fig. 6:
wherein H g For horizontal component of force at the restriction, V g For vertical component of the constraint, G is the mass of the entire cable 1, L 0 For the length of the steel cable under the relaxation state, l is the span of the steel cable, s is the Lagrange coordinate fixed on the steel cable 1, and p is the distance from any point of the steel cable 1 to the adjacent constraint. Such problems can be easily solved by referring to Cable Structures of Irvine, which is not described herein, and only the results are shown below:
eq. (15 a) shows that T varies depending on the position of the wire rope 1, and for the sake of calculation, an average method is used, and it is considered that the tension of the wire rope 1 due to its own weight is
The present embodiment studies the buffer performance of the stopper:
when the buffer performance of the stopper is researched, the adopted dynamic model is a single-degree-of-freedom model, as shown in fig. 7, the collision energy loss of the single-degree-of-freedom structure when contacting the stopper is ignored, the structural damping of the single-degree-of-freedom model is ignored, and the mechanical model with the stopper is obtained. Where M is the structural mass, x is the structural displacement, x g For ground displacement, K is the main structural stiffness, K s The stiffness of the stopper, c the stopper damping and d the initial distance between the stopper and the main structure.
For convenient numerical calculation, the parameters are assigned such that M =10kg, K =100N/M, L 0 ＝l＝1m，E＝2×10 11 Pa，A＝1×10 -4 m 2 And m =0.8kg/m, and according to the wire rope parameters, the fitted stiffness and the corresponding optimal damping can be calculated. First, it is found that the average tension is T =376.415N, the damping to be mounted is c =34.71N · s/m, and the reaction force that the wire rope 1 can provide is F (δ) =1.59 × 10, as can be seen from the fitting curve 8 δ 3 +3.2×10 4 δ 2 -318 δ. A kinetic equation can be listed according to a single-degree-of-freedom analysis model, and considering that a schematic diagram is that a limiter is installed on one side, a naveiside step function (x-d) is introduced,
initially setting d =0, vibrating the ground by a sine curve sint, solving a dynamic equation by a fourth-order Rungestota method, wherein a displacement time-course curve of a main structure is shown in FIGS. 8-12:
the displacement of the main structure on the side where the position limiter is installed is greatly smaller than that on the side where the position limiter is not installed, and the reduction is close to 95%. The time curve contrast when not installing the stopper can find that the installation stopper can not cause not ignorable impact force to the main structure because in the resilience process after the main structure contacts with the stopper, the main structure is at reverse maximum displacement and the maximum displacement when not installing the stopper is the same basically, means that the counter force that the stopper constructed to the main structure can not cause big influence to the main structure. By comparing the case where only the wire rope 1 is installed with the case where only the damper is installed, it can be found that the wire rope 1 mainly restricts displacement, and the damper mainly performs consumption of the repulsive force and reduction of vibration. When the linear spring is matched with the damper, the limiting effect of the limiter is found to be better and obvious, but when the main structure is in contact with the limiter, the main structure generates violent vibration. Although the limiting effect is better, in an actual boiler-steel frame structure, the furnace body is not required to generate any displacement, in actual engineering, the limiting device is installed on two sides, which means that if a linear spring is adopted, even if the furnace body generates tiny vibration due to wind power, the furnace body can generate violent vibration due to the existence of the limiting device, and because the mass of the furnace body is huge, the acceleration of the furnace body caused by the violent vibration can cause huge impact force on the supporting structure.
While the present invention has been described in detail and with reference to the embodiments thereof as shown in the accompanying drawings, it will be apparent to one skilled in the art that various changes and modifications can be made therein. Therefore, certain details of the embodiments should not be construed as limitations of the invention, except insofar as the following claims are interpreted to cover the invention.
Claims (1)
1. A nonlinear spring limiter containing damping for a steel frame structure of a power plant boiler is characterized by comprising a steel cable, a linear damper and a steel block; the boiler steel frame structure comprises a boiler body and a supporting frame, wherein the boiler body is suspended in the supporting frame, and the peripheries of the supporting frame are respectively provided with a cross beam at the same height; two ends of the steel cable are connected to the cross beams on two sides of the supporting frame and are horizontally arranged on one side of the furnace body at intervals; the linear damper is perpendicular to the surface of the furnace body and is connected between the steel cable and one cross beam on the front side or the rear side of the support frame; the steel block is connected to one side of the furnace body, which is adjacent to the steel cable, and the position of the steel block corresponds to that of the linear damper;
the linear damper satisfies the formula:
wherein D is any real or negative number; c represents the damping of the linear damper; t represents the tension of the steel cable, m represents the unit length mass of the steel cable, and A is the sectional area of the steel cable;
the optimal linear damper damping is achieved at D → -infinity, at which time
Left side → 2 of the left side → right side,
c at this time is the critical damping at which the free vibration decays most rapidly.
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| CN202719590U (en) * | 2012-05-23 | 2013-02-06 | 中国电力工程顾问集团华东电力设计院 | Suspension type boiler device |
| CN105544760A (en) * | 2015-12-02 | 2016-05-04 | 国核电力规划设计研究院 | Suspension type coal bunker damping structure improving heat-engine plant main workshop antivibration performance |
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| CN109519499A (en) * | 2018-12-28 | 2019-03-26 | 哈尔滨工业大学 | The determination method of quasi-zero stiffness vibration isolators vibration isolation initial frequency |
| CN110259879A (en) * | 2019-06-12 | 2019-09-20 | 北京理工大学 | For electronic Stewart structure without force feedback vibration isolation control method and system |
| DE202020000066U1 (en) * | 2020-01-10 | 2020-01-31 | Siemens Aktiengesellschaft | Electrical machine elastically attached to a frame structure |
| CN213505632U (en) * | 2020-11-16 | 2021-06-22 | 江苏富友电力机械设备有限公司 | High-stability spring support hanger |
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2022
- 2022-06-10 CN CN202210651951.XA patent/CN114934972B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202719590U (en) * | 2012-05-23 | 2013-02-06 | 中国电力工程顾问集团华东电力设计院 | Suspension type boiler device |
| CN105544760A (en) * | 2015-12-02 | 2016-05-04 | 国核电力规划设计研究院 | Suspension type coal bunker damping structure improving heat-engine plant main workshop antivibration performance |
| CN106407607A (en) * | 2016-10-27 | 2017-02-15 | 北京航空航天大学 | Airborne multi-axis vibration isolation system and optimization method thereof |
| CN207145521U (en) * | 2017-08-06 | 2018-03-27 | 袁园 | A kind of power equipment vibration absorber |
| CN109519499A (en) * | 2018-12-28 | 2019-03-26 | 哈尔滨工业大学 | The determination method of quasi-zero stiffness vibration isolators vibration isolation initial frequency |
| CN110259879A (en) * | 2019-06-12 | 2019-09-20 | 北京理工大学 | For electronic Stewart structure without force feedback vibration isolation control method and system |
| DE202020000066U1 (en) * | 2020-01-10 | 2020-01-31 | Siemens Aktiengesellschaft | Electrical machine elastically attached to a frame structure |
| CN213505632U (en) * | 2020-11-16 | 2021-06-22 | 江苏富友电力机械设备有限公司 | High-stability spring support hanger |
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