Abstracts
The simple harmonic vibration, damping vibration and forced vibration of an oscillator attached to the massless spring are always discussed in general mechanics courses. In this article, we focus on the heavy-spring conditions. We first investigate the general situation where both viscous resistance and applied force are considered under the perspective of the renormalization group theory. Then we use analytic method to study the damped oscillation of an oscillator attached to the heavy spring, where renormalization method fails to work.
Keywords:
mass-spring oscillator; damping vibration; forced oscillation
A vibração harmônica simples, o amortecimento de vibrações e a vibração forçada de um oscilador ligado a uma moal sem massa são sempre discutidos em cursos gerais de mecânica. Neste artigo, vamos nos concentrar nas condições de mola com massa. Nós primeiro investigamos a situação geral em que tanto a resistência viscosa e a força aplicada são consideradas sob a perspectiva da teoria do grupo de renormalização. Então, nós usamos um método analítico para estudar a oscilação amortecida de um oscilador ligado a uma mola com massa, em que o método de renormalização não funciona.
Palavras-chave:
oscilador massa-mola; vibração amortecida; oscilação forçada
1. Introduction
An oscillation is a common but very important phenomenon in the physical world. If a physical quantity is displaced from the equilibrium a little, linear negative feedback may then lead to an oscillation. A familiar example is a simple harmonic oscillator. Also, damping vibrations and forced vibrations of an oscillator are normally focused [1][1] L.D. Landau, E.M. Lifshitz, Mechanics: Volume 1 (Course Of Theoretical Physics) (Butterworth-Heinemann, Oxford, 1976).. The mass of the spring is neglected in models. However, the mass of the spring is unnecessarily neglected as to studying mass-spring system itself. In this article we try to solve the mass-spring system where the mass of the spring is not negligible.
In 1979, Weinstock studied the normal modes of the oscillator motion for the oscillator attached to a heavy spring by virtue of the Stieltjes integral [2][2] R. Weinstock, American Journal of Physics 47 , 508 (1979).. In 1994, da Silva obtained the normal frequencies of elastic oscillations of a particle suspended on a spring of non-negligible mass again under the perspective of the renormalization group theory [3][3] J.M N. da Silva, American Journal of Physics 62 , 423 (1994).. A continuous spring can be regarded as a chain of many small springs coupling an equal amount of small masses. Then mapping process is repeated by associating two consecutive small springs into a single one. At last, only the boundary effect matters. JM Nunes dealt with the problem only for the simplest situation, without the friction and applied force, thus the advantage of this method does not emerge in this case. In fact, we can not only find out the normal frequencies in the conservative system, but also obtain the specific equation of motion when external forces are acted on.
In the next sections, we first explore the most general condition, a forced vibration with viscous resistance, using the renormalization method. Then we deal with a special case analytically where the renormalization method fails to work. We investigate the orthogonality of the solutions of the PDEs in base set, and then obtain the motion of the damping oscillator attached to a heavy spring.
2. The forced mass-oscillator with damping
Hang an uniformly distributed spring with mass m vertically. The top side is fastened to stable fixture and the bottom side concatenate an object with mass M as oscillator. The free length of spring is L and the stiffness coefficient is k. To be discretized, the heavy spring is viewed as a series of small non-mass N equal springs and each small spring is coupled with a concentrated object with mass m/N. The natural length and elastic constant (labeled by s) of each small spring are L/N and s = kN respectively. The damping on the oscillator M can be calculated as if the velocity of oscillator is and damping coefficient is b. Besides, a time-dependent force f(t) is applied on the oscillator.
The positions of objects are denoted by , then equations of motion can be set up as
We can eliminate the constant terms derived from gravity in the Eq. (1) by changing the coordinates appropriately. So that we can use newly defined coordinates ( ) to describe the motion (da Silva proposed a way to approach these newly defined coordinates [3][3] J.M N. da Silva, American Journal of Physics 62 , 423 (1994).). The equations with new coordinates are written as follows, If we denote and then the Eq. (2) can be Fourier transformed as with and .By Eq. (3), we get and . We combine two small springs into a bigger small spring. That is, with this mapping process, the previous and springs now become the bigger small spring. The new Fourier transformed position function of spring is denoted by and . So we have
Comparing Eq. (4) and Eq. (3), the equations change regularly2 2 After each iteration, the coefficients of left terms in Eqs. (4b) and (4c) update to c(l+1)=c(l)2-2 and C(l+1)=c(l)C(l)-1 from c(l) and C(l). after the process of combining two consecutive small springs into bigger spring. So we repeat the combination to renormalize. If we set , then after repeat, Eq. (4c) finally becomes . and the position function of the oscillator is
The next thing to do is to find out the iteration value and . Comparison between Eqs. (3) and (4) gives and , so and more generally,
Introduce and let . and are easily accessible with this variable substitution, i.e., . Finally, . Notice that , so and . By Eq. (5), Then (neglect because of ) due to . It's the motion equation of the oscillator with consideration of mass of spring, external forces including damping, gravity and applied time-dependent force.3 3 Notice that ∫-∞∞∫-∞∞f(t)e-iωtdtiωb-Mω2+cot(ωmk)ωkmeiωtdω=∫∞-∞∫-∞∞f(t)e-i(-ω)tdti(-ω)b-M(-ω)2+cot((-ω)mk)(-ω)kmei(-ω)td(-ω), so ∫-∞∞∫-∞∞f(t)e-iωtdtiωb-Mω2+cot(ωmk)ωkmeiωtdω=∫-∞∞∫-∞∞f(t)eiωtdt-iωb-Mω2+cot(ωmk)ωkme-iωtdω and uoscillator(t) is pure real. But one thing to note here is that f(t) can not be 0 or the solution vanishes. We deal with this condition in following part.In fact, if ,4 4 By limm→0cotωmk=km/ω, we have limm→0G(ω)=1iωb-Mω2+k, which is consistent with the transfer function G(s)=1Ms2+bs+k for standard 2nd order mass/spring/damper system by Laplace transformation. [4] There is also another conclusion if we add one more expansion term in cotx (cot≃1x-x3-x345+... within radius of convergence), limm→0cotωmk=km/ω-13ωmk, hence limm→0G(ω)=1iωb-Mω2+k-13mω2). In no viscous case (b = 0), revised natural circular frequency for spring mass system is ω=kM+m/3) where spring's effective mass is m/3, [5] which can be obtained from limm→0G(ω)=1-(M+m/3)ω2+k. the motion equation of the oscillator can be given by the convolution of f(t) and g(t), i.e.. From the following discussion, we will know that the frequencies which satisfy , which make divergent and lead to resonance, are exactly eigenvalues in no applied force condition (see Eq. (9)).
3. No applied force condition
Since we can no longer use renormalization method for no applied force condition, we then use mathematical physics equations to study this problem. Adopt appropriate coordinates as introduced before, and the problem can be analytically described as follows.5 5 Take infinitesimal spring with length dx, stiffness coefficient kLdx and mass dxLm. The position deviation of infinitesimal spring from equilibrium is denoted by du. Then motion equation of the infinitesimal spring can be given by ∂(kLdxdu)∂xdx=dxLm⋅d2udt2 according to Newton's second law.
We consider using method of separation of variables to solve this equation and we take as the ansatz. The equations above then become By Eqs. (8a) and (8b), we substitute into Eq. (8c) and get the eigenvalue equation We set that and are different solutions from the base set. To obtain expansion coefficients from initial conditions (8d) and (8e), we first derive the orthogonality relation between bases and within the boundary condition (8c). According to Eqs. (8a) and (8c), we haveCalculate Eq. (10b) Eq.(10d) and we get
From Eq.(11) we eventually reach the following equality under the boundary condition (8c), Eq. (12) shows that the solutions in the base set are generalized orthogonal [6][6] Tyn Myint-U, Partial Differential Equations of Mathematical Physics (North-Holland, New York, 1973).. The squared norms (denoted by N2) of the eigenfunctions can be calculated as So the solution to the Eq. (7) can be written as ; the expansion coefficients are determined by and collectively. We then expand and based on the orthogonality relation (12): whereLet , then
Comparing Eq. (15a) + Eq. (15b) with , we get Hence, and . Finally can be given as where is determined by the initial conditions both and .6 6 If ϕ(x) and ψ(x) are dependent, to be more precise, Pn=Qn, χ can be any value. In this case, either Eq. (14a) or Eq. (14b) can be equally used to calculate the expansion coefficient An, and don't bother to introduce χ. For the simple but most common case, if , i.e., we have (hence ). According solutions satisfy Eqs. (7) when .The eigenvalue equation reveals as (eigenvalue won't be 0). Notice that is also eigenvalue if is eigenvalue. The corresponding expansion coefficients have the relation and due to the Eq. (14). Considering ,
Eq. (18) verifies that both and are pure real when ansatz is taken. Of course is also pure real. We can obtain two types of independent eigen-vibration modes from this result. Let 7 7 It's hard to find all μs analytically from cotμL=ibkm+μMLm but we can use perturbation to investigate since imaginary part in RHS of eigenvalue equation. bkm is feeble in generally underdamping conditions. The zero-order approximation, μ(0)tanμ(0)L=mML for zero friction situation (b= 0), is discussed in previous work [2]. Obviously, solutions are real numbers and come in pairs (-μ(0) is also solution if μ(0) satisfies zero-order eigenvalue equation). Perturbation calculation shows the first order modification is negative pure imaginary number and the paired zero-order eigenvalues ±μ(0) share the same first order modification. It coincides with the previous analysis that -μ¯ is eigenvalue if μ is eigenvalue. , then The two types of independent vibration modes are given by8 8 To get a more detailed understanding of exp(-ζnLkmt), we use cotz≃1z-z3-z345+... again within the radius of convergence. The first-order approximation of cot(ξn-iζn) in eigenvalue equation gives that ζnξn=b/2MkmξnL, so the dumping factor is exp(-bt∕2M), which is the same as the damping factor of common damped oscillators. [1] The second-order approximation shows that the dumping factor is exp[-bt/2(M+m/3)]. The oscillator (x= L) vibrates with damped amplitude (as is shown in Fig. 2) in both types of modes, which is reasonable.A discretization model. The heavy spring with natural length L, mass m and stiffness coefficient k is divided into N small springs coupled with concentrated objects.
Let be dimensionless with , the eigen-vibration mode of the oscillator can be plotted under two cases with and . The oscillator vibrates with damped amplitude.
For zero-friction case (b = 0), the solutions to eigenvalue equation are pure real, i.e.. Then two types of vibration modes become9 9 With tanξnL=mMξnL, the frequency ξnLkm degrades if we neglect the mass of the spring, i.e.limm→0ξnLkm=kM for all ξn. Thus, many degrees of freedom are reduced in one body problem, ω=kM.
Summarize the result: the solution to Eq. (7) is where eigenvalue is given by Eq. (9). Expansion coefficient and squared norms are given by Eqs. (17) and (13).
4. Conclusion
In this article, we detailedly studied the vibration of spring oscillator when the mass of the spring can't be neglected. Damped oscillation and forced vibration are especially focused. For general condition, oscillation with friction and applied force, renormalization method is employed to obtain the equation of the motion. Renormalization method shows superiority when applied force f(t) exerts on the oscillator. We also investigate the damping vibration without applied force with theory of partial differential equations. For given boundary condition, the generalized orthogonality of base set is studied. We discussed the characters of the eigenvalue and the expansion coefficient and the discussions verified the validity of the solution.
- 2
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3
Notice that , so and is pure real.
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4
By , we have , which is consistent with the transfer function for standard 2nd order mass/spring/damper system by Laplace transformation. [4][4] S.M. Shinners, Modern Control System Theory and Design (John Wiley & Sons, New York, 1998). There is also another conclusion if we add one more expansion term in ( within radius of convergence), , hence ). In no viscous case (b = 0), revised natural circular frequency for spring mass system is ) where spring's effective mass is m/3, [5][5] Y. Yamamoto, Journal of Sound and Vibration 220 , 564 (1999). which can be obtained from .
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5
Take infinitesimal spring with length dx, stiffness coefficient and mass . The position deviation of infinitesimal spring from equilibrium is denoted by . Then motion equation of the infinitesimal spring can be given by according to Newton's second law.
- 6
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7
It's hard to find all s analytically from but we can use perturbation to investigate since imaginary part in RHS of eigenvalue equation. is feeble in generally underdamping conditions. The zero-order approximation, for zero friction situation (b= 0), is discussed in previous work [2][2] R. Weinstock, American Journal of Physics 47 , 508 (1979).. Obviously, solutions are real numbers and come in pairs ( is also solution if satisfies zero-order eigenvalue equation). Perturbation calculation shows the first order modification is negative pure imaginary number and the paired zero-order eigenvalues share the same first order modification. It coincides with the previous analysis that is eigenvalue if is eigenvalue.
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8
To get a more detailed understanding of , we use again within the radius of convergence. The first-order approximation of in eigenvalue equation gives that , so the dumping factor is , which is the same as the damping factor of common damped oscillators. [1][1] L.D. Landau, E.M. Lifshitz, Mechanics: Volume 1 (Course Of Theoretical Physics) (Butterworth-Heinemann, Oxford, 1976). The second-order approximation shows that the dumping factor is .
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9
With , the frequency degrades if we neglect the mass of the spring, i.e. for all . Thus, many degrees of freedom are reduced in one body problem, .
References
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[1]L.D. Landau, E.M. Lifshitz, Mechanics: Volume 1 (Course Of Theoretical Physics) (Butterworth-Heinemann, Oxford, 1976).
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[2]R. Weinstock, American Journal of Physics 47 , 508 (1979).
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[3]J.M N. da Silva, American Journal of Physics 62 , 423 (1994).
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[4]S.M. Shinners, Modern Control System Theory and Design (John Wiley & Sons, New York, 1998).
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[5]Y. Yamamoto, Journal of Sound and Vibration 220 , 564 (1999).
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[6]Tyn Myint-U, Partial Differential Equations of Mathematical Physics (North-Holland, New York, 1973).
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[7]M.S. Santos, E.S. Rodrigues and P.M.C. de Oliveira, American Journal of Physics 58 , 923 (1990).
Publication Dates
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Publication in this collection
Oct-Dec 2015
History
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Received
19 July 2015 -
Accepted
31 Aug 2015