Abstract
Microscale and nanoscale mechanical resonators have recently emerged as ubiquitous devices for use in advanced technological applications, for example, in mobile communications and inertial sensors, and as novel tools for fundamental scientific endeavours. Their performance is in many cases limited by the deleterious effects of mechanical damping. In this study, we report a significant advancement towards understanding and controlling supportinduced losses in generic mechanical resonators. We begin by introducing an efficient numerical solver, based on the 'phonontunnelling' approach, capable of predicting the designlimited damping of highquality mechanical resonators. Further, through careful device engineering, we isolate supportinduced losses and perform a rigorous experimental test of the strong geometric dependence of this loss mechanism. Our results are in excellent agreement with the theory, demonstrating the predictive power of our approach. In combination with recent progress on complementary dissipation mechanisms, our phonontunnelling solver represents a major step towards accurate prediction of the mechanical quality factor.
Introduction
Mechanical coupling of a suspended structure to its supports is a fundamental energy loss mechanism in micromechanical and nanomechanical resonators^{1}. Referred to variously as clamping^{2} or anchor loss^{3}, this process remains significant even in devices fabricated from highquality materials operated in vacuum and at cryogenic temperatures, and is in fact unavoidable in any nonlevitating system. Although much progress has been made towards the understanding of mechanical dissipation at the microscale and nanoscale^{2,4}, obtaining reliable predictions for the fundamental designlimited quality factor, Q, remains a major challenge while direct experimental tests are scarce^{5,6,7}. At the same time, the implementation of highquality micromechanical and nanomechanical systems is becoming increasingly important for numerous advanced technological applications in sensing and metrology, with select examples including wireless filters^{3,8}, onchip clocks^{9}, microscopy^{10,11,12,13} and molecularscale mass sensing^{14,15}, and recently for a new generation of macroscopic quantum experiments that involve mesoscopic mechanical structures^{16,17,18,19,20,21,22,23}. Here, we introduce a finiteelementenabled numerical solver for calculating the supportinduced losses of a broad range of lowloss mechanical resonators. We demonstrate the efficacy of this approach via comparison with experimental results from microfabricated devices engineered to isolate supportinduced losses by allowing for a significant variation in geometry, while keeping other resonator characteristics approximately constant. The efficiency of our solver results from the use of a perturbative scheme that exploits the smallness of the contact area, specifically the recently introduced 'phonontunnelling' approach^{24}. This results in a significant simplification over previous approaches and paves the way for CADbased predictive design of lowloss mechanical resonators.
The origins of mechanical damping in microscale and nanoscale systems have been the subject of numerous studies during the last decades, and several relevant mechanisms for the decay of acoustic mechanical excitations, that is, phonons, have been investigated^{2,4}. These include: (i) fundamental anharmonic effects such as phonon–phonon interactions^{4,25}, thermoelastic damping (TED)^{4,25,26,27,28} and the Akhiezer effect^{4,25}; (ii) viscous or fluidic damping involving interactions with the surrounding atmosphere or the compression of thin fluidic layers^{29,30,31}; (iii) material losses driven by the relaxation of intrinsic or extrinsic defects in the bulk or surface of the resonator^{32,33,34,35,36,37} for which the most commonly studied model is an environment of twolevel fluctuators^{38,39} and (iv) supportinduced losses, that is, the dissipation induced by the unavoidable coupling of the resonator to the substrate^{3,7,8,40,41}, which corresponds to the radiation of elastic waves into the supports^{5,6,24,42,43,44}. This last mechanism poses a fundamental limit, as vibrations of the substrate will always be present.
These various dissipation processes add incoherently such that the reciprocals of the corresponding Qvalues satisfy 1/Q_{tot}=∑_{i}1/Q_{i}, where i labels the different mechanisms. Thus, in a realistic setting, care must be taken to isolate the contribution under scrutiny. In contrast to all other damping mechanisms (i–iii), which exhibit various dependencies with external physical variables such as pressure and temperature, supportinduced dissipation is a temperature and scaleindependent phenomenon with a strong geometric character that is present in any suspended structure. Moreover, its scale independence implies that the same analysis can be applied to both microscale and nanoscale devices. We exploit this geometric character to isolate the supportinduced contribution and obtain a direct experimental test of phonontunnelling dissipation.
The numerical solver we introduce provides a new technique to efficiently model supportinduced losses for a broad class of mechanical structures. Previous approaches have relied on either the direct solution of an elastic wave radiation problem involving the substrate^{6,7,42,43,44} or the simulation of a perfectly absorbing artificial boundary^{5,41}, with systematic tests as a function of geometry limited to a few specific cases^{5,6,7}. In contrast, our technique represents a substantial simplification in that it reduces the problem to the calculation of a perfectly decoupled resonator mode together with free elastic wave propagation through the substrate in the absence of the suspended structure. A key feature of our method is to combine a standard finiteelement method (FEM) calculation of the resonator mode together with the use of an extended contact at the support. This allows us to treat complex geometries, taking proper account of interference effects between the radiated waves.
In summary, we develop and test an efficient method for calculating the clamping loss of highQ mechanical resonators. Our analysis includes a thorough experimental verification of this theoretical framework by employing resonators that are specifically designed to isolate the clampingloss contribution to the total dissipation 1/Q. The measured damping in these structures matches the theoretical predictions and demonstrates in a direct manner the strong geometric character of this fundamental dissipation channel.
Results
Phonontunnelling approach
In analogy to radiation tunnelling in photonics and electron tunnelling in lowdimensional structures, we adopt a 'phonon tunnelling' picture to describe the supportinduced losses^{24}. In this picture, the mechanical resonance of interest, characterized by frequency ω_{R}, is regarded as a phonon cavity that is weakly coupled to the exterior by a hopping process, whereby the elastic energy leaks out of the resonator through the narrow contact areas from which it is suspended. Within this framework, one can start from the harmonic Hamiltonian associated with the elastic scattering eigenmodes of the entire structure, including the substrate, and derive a quantum model for the Brownian motion experienced by each resonance of the suspended structure.
The corresponding weak tunnel couplings can be obtained to lowest order in the small parameter k_{R}d, where 1/k_{R} is the characteristic length scale over which the resonator mode varies appreciably and d is the characteristic dimension of the contact area S from which the resonator is suspended. For typical structures that exhibit highQ mechanical resonances, k_{R}d≪1 is comfortably satisfied. This justifies the weak coupling approximation and leads to a general expression for the associated dissipation 1/Q in terms of the 'overlaps' between the scattering modes and the resonator mode. In the limit d→0, the leading contribution is obtained by replacing the scattering modes by the free (unperturbed) modes of the supports, which yields^{24}
Here, and are the stress and displacement fields associated with the normalized resonator mode, and are the analogous fields for the continuum of support modes labelled by q (eigenfrequencies ω(q)), and ρ_{s} and ρ_{R} are, respectively, the densities of the substrate and resonator materials. The resonator mode should satisfy either (i) free or (ii) clamped boundary conditions at the contact area, S, depending on the behaviour of the eigenmode when S is small, whereas the unperturbed support modes should satisfy the converse. These homogeneous boundary conditions correspond, respectively, to and so that only one of the two terms in the surface integral is finite. In general, the decomposition between 'resonator volume' and 'supports' consistent with the weak coupling condition need not be unique. Examples of case (i) are pedestal geometries, such as microspheres, microdisks or microtoroids, when the pedestal is included in the support^{24}. It is worth noting that for these geometries, if the pedestal is assumed to have perfect impedance match with the substrate, equation (1) leads to a particularly simple result for the Q of an axially symmetric resonance^{7},^{24}, which has been verified in ref. 7 for the radial breathing mode of microtoroid structures. On the other hand, examples of case (ii) include the planar structures investigated here, when the resonator volume consists of the portion of the structure that is freestanding.
A rigorous derivation of equation (1) is given in ref. 24. Alternatively, if one uses a decomposition of the displacement field in terms of the unperturbed support modes and the discrete modes of the resonator volume, equation (1) follows simply from applying Fermi's Golden rule to phonon decay, with the interaction Hamiltonian between the resonator volume (labelled <) and the surrounding supports (labelled >) given by for case (i) and for case (ii). Within this framework, it is straightforward to realize that the validity of equation (1) is more general than the condition k_{R}d≪1 and will also apply to any resonance, for which the supportinduced frequency shift is small compared with the relevant mode spacing (that is, the free spectral range at the corresponding resonant frequency) so that the weak coupling assumption is warranted. For our case, the use of this master formula is completely equivalent to previous intuitive approaches based on forcing the substrate with the stress source generated by the resonator mode^{6},^{42},^{43},^{44}, as can be shown rigorously by using—for the elastic Green's function of the substrate—a spectral decomposition in terms of its free modes. In the presence of mode coupling^{5,7} not induced by disorder, our treatment remains valid provided that the mode mixing is not dominated by supportinduced interactions, which includes the case where it is accounted for by FEM assuming perfect clamping and excludes cases where symmetry breaking induced by the support is relevant. Finally, one should note that in the weakcoupling regime, it is straightforward to incorporate mode coupling not accounted for by the FEM into our phonontunnelling formalism.
Qsolver
Though the aforementioned framework is completely general, to investigate the predictive power of our approach, we focus specifically on the flexural modes of a symmetric plate geometry of thickness t that is inscribed in a circle of radius R, with the contact area S corresponding to the outer rim of an idealized circular undercut (undercut distance of L_{und}). To calculate the theoretical Qvalues of such devices via equation (1), we have developed a numerical solution technique that determines the normalized resonator eigenmode and eigenfrequency via FEM (with at S) and is based on a decomposition into cylindrical modes for the support, which is approximated by the substrate modelled as an isotropic elastic halfspace. The latter approximation is expected to be quantitatively precise for the lowlying flexural resonances when the underetched gap between the suspended structure and the substrate satisfies h<R (where h is the gap height), and the largest resonant wavelength for elastic wave propagation in the substrate is smaller than the relevant length scales characterizing the mounting of the sample (see below). The aforementioned weakcoupling condition, k_{R}d≪1, follows in this case from t≪R. From equation (1), exploiting the fact that the eigenmodes of an elastic halfspace are given by straightforward analytical expressions^{45}, we obtain (see Methods section for details of this derivation)
Here, we introduce the dimensionless functions , and the linear stress Fourier components with n=0, ±1, ±2, .... The different types of relevant planewave modes of the halfspace^{45} (that is, longitudinal (l), transverse vertical (t) and surface acoustic waves (s) given that transverse horizontal waves do not contribute) are labelled by γ=l, t, s with c_{γ}, the corresponding speed of sound—as determined by the density ρ_{s}, Poisson ratio ν_{s} and Young's modulus E_{s} of the substrate. We adopt spherical coordinates for the incident wave vector with polar angle θ and cylindrical coordinates for the position . The squared displacements are given by analytical expressions, that only depend on γ, cosθ and ν_{s}^{24,45}, which lead to straightforward integrals for the functions detailed in the Methods section.
If one considers low frequency modes that are symmetric with respect to both the x−z and y−z planes so that f_{z,0}≠0 and ω_{R}≪c_{γ}/R ∀γ, one can approximate the series in equation (2) by the n=0 term with the evaluated at . For a Poisson ratio ν_{s}=1/3, this yields the following approximation
where f_{z,0} corresponds to the total force applied on the contact area S. For the typical micromechanical resonators analysed here (see below), this approximation deviates from equation (2) by 20%. Finally, we highlight that it is straightforward to generalize the above to inplane modes and the rim need not be continuous, as in cases where the resonator volume makes contact with the support at a disjoint set of small areas (for example, a bridge geometry with no undercut).
Free–free design
To experimentally verify our solver, we have developed 'free–free' micromechanical resonators consisting of a central plate (resonator) of length L and width w suspended by four auxiliary beams as depicted in Figure 1a. These structures are etched from a highreflectivity monocrystalline distributed Bragg reflector (DBR)—as described in the Methods section, suited for Fabry–Perotbased optomechanical systems^{46}. The devices used in this study constitute a variant of the previously demonstrated free–free flexural design in which auxiliary beams with widths w_{s}≪w and lengths L_{s}=λ_{t}/4 (where λ_{t} is the resonant wavelength for the propagation of torsional waves) placed at the nodes of the central resonator mode provide noise filters to suppress supportinduced losses^{3}. A major drawback with the λ_{t}/4beam design is that the resulting auxiliary beam length can be excessive. In fact for the eigenfrequencies investigated in this work, the corresponding beam length (>400 μm at 1.7 MHz) leads to proliferation of lowfrequency flexural resonances that compromise the stability of the optical cavity and render mode identification difficult. We circumvent this issue by utilizing instead a reduced length L_{s}≪λ_{t}/4 chosen to avoid spectral overlap between the free–free resonance and flexural resonances of the auxiliary beams.
The free–free design provides an ideal platform to isolate and measure phonon tunnelling dissipation: first, by altering the attachment position of the auxiliary beams, this design allows for a significant variation of geometry, while approximately preserving the frequencies and effective surfacetovolume ratios of the resonators. As these characteristics are kept constant, one can rule out the influence of additional damping mechanisms (specifically those driven by internal losses and surface effects) on the variation in Q and hence isolate supportinduced losses in the measured devices. Second, the free–free resonators provide an intuitive illustration of the strong geometric character of the supportinduced dissipation. Heuristically, the clamping loss will be proportional to the elastic energy radiated through the auxiliary beams, which should approximately scale as the squared deflection of their contacts with the central resonator (see Fig. 1b,c). Thus, varying the contact position of the auxiliary beams results in a characteristic modulation of the damping rate, which approximately maps out the central resonator mode shape (Fig. 1b). As expected, the minimumloss design corresponds to the geometry in which the auxiliary beams are attached at the nodes of the fundamental resonance of the central resonator. It is interesting to note that the theoretical clamping loss limit 1/Q_{th} for nodal positioning is always finite as described in Figure 1c. In turn, for generic placement away from the nodal points, one obtains for the improvement in Q with respect to the clamped–clamped configuration the heuristic relation Q_{f−f}/Q_{c−c}∼(w/2w_{s})^{2}, which assumes that ω_{R} and the effective mass m_{R} are the same for both configurations and ω_{R} lies away from the flexural resonances of the auxilliary beams. This figure of merit can be derived from equation (3), if one uses the approximate scalings and , which follow from neglecting the undercut, using thinplate elasticity, and exploiting the fact that w_{s}≪L to analyse the elastic wave propagation in the auxilliary beams^{24}.
Measured dissipation
To identify the mechanical modes of our microfabricated resonators (see Figure 2a for an example of a completed device), we compare the optically measured resonator frequencies, as a function of the auxiliary beam position, with the theoretical eigenfrequency variation. The simulated values are generated using the geometric parameters determined via careful analysis of the completed resonators (see Supplementary Method). As can be seen in Figure 2b, in addition to the symmetric free–free resonance, there is also an antisymmetric eigenmode with comparable frequency. We observe no mode coupling between these resonances, which is consistent with the specific mirror symmetries of the structure. The frequencies are accurately reproduced by the FEM simulation, if we allow for frequency offsets that are solely dependent on the mode parity (262 kHz offset for the free–free mode and 89 kHz offset for the antisymmetric mode). We attribute these shifts to a materialrelated dissipation mechanism involving both surface and bulk contributions (see Supplementary Method for further details).
All dissipation measurements have been performed at high vacuum (10^{−7} mbar) and at cryogenic temperatures (20 K) to suppress fluidic and thermoelastic damping in the devices (Fig. 2c,d). Under these conditions, we record quality factors spanning 1.4×10^{4} to 5.1×10^{4}, with the minimum Q corresponding to the free–free mode of devices with an auxiliary position of 62.5 μm and R=116 μm, and with the maximum Q to the geometry closest to nodal positioning (37.4 μm) for the same radius and type of mode (see Fig. 3). For the symmetric mode, we readily observe the expected characteristic modulation in Q as a function of the placement of the auxiliary beams with a relative variation of ΔQ_{exp}/Q_{exp}∼260% (∼80%) for R=116 μm (R=131 μm). At the same time, the use of the free–free geometry ensures that the frequency variation is kept small, with a range of Δf/f∼20% (∼10%). In contrast, the Qvalues for the antisymmetric mode are nearly constant with Q≈2.1×10^{4} (Fig. 3c). This is expected as the theoretical supportinduced loss for this mode is negligible. Additionally, as this resonance involves mainly deformations of the auxiliary beams, its dissipation is not correlated with the mode shapes of the central resonator. The damping of this mode is instead dominated by other sources of dissipation, most likely by the materialrelated losses that are also responsible for the frequency shifts. Thus, we obtain an independent corroboration that the characteristic Qvariation observed for the free–free mode is indeed induced by the modification of the geometry rather than by the small frequency variation present in the devices.
Discussion
To quantitatively compare the measurements with our numerical predictions, two issues must be considered: (i) our model only captures supportinduced losses, although other loss mechanisms may still contribute to the overall damping in the devices and (ii) the parameters for the halfspace model of the substrate must be properly chosen. Consideration (i) together with the fact that we have designed sets of resonators for which the frequencies and effective surfacetovolume ratios are kept approximately constant implies that any additional damping mechanism that is relevant at low temperatures and high vacuum, but is insensitive to the variation in geometry, should contribute a constant offset 1/Q_{*} in the measured dissipation 1/Q_{tot}. Consideration (ii) is nontrivial given the longwavelength nature of the elastic waves radiated into the substrate. For an average resonator frequency of 2.12 MHz, estimates of the maximum wavelength for the freely propagating elastic waves yield a value of 2.5 mm, which largely exceeds the wafer thickness (300±25 μm). Thus, the mechanical material parameters for the substrate should be determined by the properties of the underlying stage and positioning mechanism in the cryostat rather than those of the chip itself. Hence, we assume for the halfspace the mechanical properties of polycrystalline commercially pure (grade 2) titanium (see the caption of Figure 3 for more details), of which the bulk of the structure beneath the resonator consists. Taking all of this into account, the theory shows remarkable agreement with the measured dissipation (as shown in Fig 3). It is important to note that the only free parameter used in the model of the free–free mode is a constant offset of 1/Q_{*}=2.41×10^{−5}. Although the exact nature of the corresponding dissipation mechanism is currently unknown, we assume that it arises from material losses in the resonator epistructure.
It should be noted that most commercially viable resonators operate in a regime where TED dominates, and in some instances, intuitive understandings of the supportinduced damping^{3,8,40} have allowed for its suppression below other limiting damping mechanisms. Nonetheless, if current efforts to minimize TED in such structures at room temperature are successful^{28}, supportinduced losses may pose the next challenge for maximizing Q. On the other hand, in fundamental research thrusts employing high vacuum and cryogenic systems, supportinduced losses can become a dominant factor^{7,41}. For example, the free–free designs explored here provide a route to minimize supportinduced losses for application in optomechanical experiments utilizing the micromechanical resonator as an end mirror in a highfinesse Fabry–Perot cavity^{46}. To gauge the relevance of our 'free–free' micromirror design in this context, it is instructive to compare the fundamental limit at nodal positioning Q_{th}≈5×10^{6} and the maximum measured Qvalue of 5.1×10^{4} with the corresponding results for the fundamental flexural mode of a clamped bridge of comparable dimensions. In fact, for the typical dimensions considered, as required for integration in a highperformance Fabry–Pérot cavity, we obtain a theoretical limit Q_{c−c}∼10^{3} in line with previous measurements on monocrystalline DBR optomechanical structures^{47}.
Given the scaleindependent nature of supportinduced losses, our solver can be applied equally well to nanoscale mechanical devices. We find that for a recent demonstration of a nanomechanical doubly clamped beam coupled to a superconducting qubit at milliKelvin temperatures^{48}, the measured values for the resonator's maximum Q (≈6×10^{4}) can be understood solely via the phonontunnelling loss model (beam geometry of 0.3×0.18×6 μm; M. LaHaye, private communication), which predicts a Qvalue of 5.4×10^{4}, in excellent agreement with the experimental value. In addition, the phonontunnelling framework is also applicable to prestressed nanoresonators such as Si_{3}N_{4} strings^{34} or membranes and has recently been experimentally verified for the latter^{49}.
In conclusion, we have developed an efficient FEMenabled numerical method for predicting the supportinduced dissipation in microscale and nanoscale mechanical resonators. In combination with existing models for other relevant damping channels (for example, fluidic and TED^{27,28}), our 'phonontunnelling' solver makes further strides towards accurate prediction of Q. Furthermore, we provide a stringent experimental test of the corresponding theory using resonators engineered to isolate supportinduced losses. Our results unambiguously demonstrate that phonontunnelling plays a significant role in the mechanical dissipation of these devices and illustrate the strong geometric character of this fundamental damping mechanism. Finally, we note that as the weakcoupling approximation underlying our treatment is more general than the condition of small contact area, our numerical solver can in principle be extended to other relevant scenarios such as phononicbandgap structures^{41}.
Methods
Numerical calculation of Qvalues
To derive equation (2) from equation (1), we adopt for the free elastic halfspace^{45}, modelling the decoupled support, a decomposition into eigenmodes (with n=0, ±1, ±2, ...) that have axial symmetry with respect to z (see Fig. 1). These are related to the plane wave eigenmodes by
where we adopt spherical coordinates for the incident wavevector (θ=π/2 for γ=s and θ≤π/2 otherwise). We note that for the suspended plate geometry considered, the appropriate resonator mode satisfies at the contact S so that we need to evaluate the second term in equation (1).
The thinplate condition t≪R directly allows us, given the flexural nature of the modes of interest, to neglect stresses at S that are parallel to the substrate, with the possible exception of bendingmoment contributions^{45}—this also applies if there are small transverse dimensions comparable to t. However, the bendingmoment contributions also become negligible in the limit t/R→0, as can be shown by using: (i) that, given ω_{R}≪c_{γ}/R ∀γ, we can Taylor expand at the origin in the integral over S, (ii) that we can assume relevant stresses to be concentrated around the ends of the auxiliary beams so that the bending moments at S are mostly oriented along y, (iii) the reflection symmetries with respect to the y−z (operator ) and x−z (operator ) planes and (iv) that, barring interference effects, these bendingmoment contributions are at most of relative order^{24} k_{R}t—here is the resonant wavevector for the propagation of flexural waves. Thus, we find that for all mode types other than −+ (antisymmetric (symmetric) with respect to ()), the correction associated to neglecting the bending moments scales as ΔQ/Q∼(k_{R}t)^{2}, whereas for −+ modes, it scales as ΔQ/Q∼(k_{R}t) (note that L∼R). In turn, we find that the relative error in using equation (1), arising from the weakcoupling approximation, scales in this case as ΔQ/Q∼Δω_{R}/ω_{R}∼Δ_{I}(ω_{R})/2ω_{R}∼(k_{R}t)^{3}, where the phonontunnellinginduced frequency shift Δω_{R} is approximated by where I(ω) is the environmental spectrum^{24}.
Hence, we can assume and neglect the variation of across the thickness t (that is, the zdependence at S), so that the support modes only enter into equation (1) through . To determine the latter, we adopt cylindrical coordinates , exploit that reflection at the free surface preserves the tangential component of the wavevector implying
and use the Bessel integral
Thus from equations (4,5,6), we obtain
where we have also used that is independent of ϕ. Subsequently, substitution of equation (7) into equation (1) leads to equation (2) after using that here
where d_{γ} is the dimensionality (that is, d_{γ}=3 for γ≠s and d_{γ}=2 for γ=s), performing the substitution ω=c_{γ}q (for each γ), and integrating over ω. Finally, substitutionof the explicit expressions for the plane wave eigenmodes (see for example Appendix A in ref. 24) and ν=cosθ into the definition of allows us to obtain:
where we use the ratio α≡(c_{t}/c_{l})^{2}=(1−2ν_{s})/2(1−ν_{s}) for the supports' material (ν_{s} is the corresponding Poisson ratio). In turn, ξ(α) is the ratio of the propagation velocity of surface waves to c_{t}, which is always less than unity^{45}, and
The sum in equation (2) can be reduced to a sum over n≥0 by noting that J_{−n}(x)=(−1)^{n}J_{n}(x) and that as the resonator mode is real, the linear stress Fourier components satisfy . Furthermore, the length of the central resonator L is comparable to the radius R, and we focus on lowlying resonances of the suspended structure so that the aforementioned condition ω_{R}≪c_{γ}/R ∀γ is always satisfied. This implies for m>n and , which can be understood by considering the behaviour of the Bessel functions for small arguments. Thus, we find that in equation (2), the sum over the index n is dominated by the first nonvanishing term as determined by the reflection symmetries . The latter also imply (n=0, 1, 2, ...):
where the resonator mode of type α,β satisfies and . To efficiently extract the above from the FEM simulation, we convert them into volume integrals using an adequate Gaussian weight so that, for example, for a fully symmetric mode, we have
where we again use cylindrical coordinates and V denotes the resonator volume. In addition, we exploit that the reflection symmetries naturally allow to perform the FEM simulation on a single quadrant. Thus, numerical evaluation can be conveniently performed using a fixed a_{*} and a mesh size M such that (V/4 M)^{1/3}<a_{*}≪t. We have checked the convergence and estimate the numerical error to be of order 5%.
Numerical simulations of the resonator mode are performed with the aid of COMSOL multiphysics. Accurate threedimensional CAD models representing the resonator geometry are generated using Solidworks (matched with highquality scanning electron microscope images as described in Supplementary Method), and the bidirectional interface between the two programs is exploited to perform a parametric sweep of the auxiliary beam contact position for determining the pertinent information about the relevant mode, namely its eigenfrequency, linear stress Fourier components f_{z,n} and normalization constant. In this instance, a single CAD file is used with a global variable incorporated to control the lateral position of the auxiliary beams with respect to the centre of the central resonator. We use for the mechanical properties of our singlecrystal resonators an anisotropic material model incorporating the elastic stiffness matrix for the epitaxial structure as obtained from a weighted average between the relative content of GaAs and AlAs (46.37% GaAs/53.63% AlAs). The corresponding parameters are: C_{11}=119.6 GPa, C_{12}=55.5 GPa, C_{44}=59.1 GPa and ρ_{R}=4,483 kg m^{−3}. The resonator axes are aligned along 〈100〉 (zincblende structure). Note that we ignore the 6° misorientation of the germanium substrate, as we have checked that it has a negligible impact (error of 0.3%) on the simulated frequency response of the resonators. Finally, as a nontrivial check, we have applied our numerical method to bridge geometries with no undercut for which a simple analytic expression is valid in the limit of large aspect ratio (see Supplementary Method).
Epitaxial material structure and resonator fabrication procedure
The layer structure for our high reflectivity resonators consists of 40.5 periods of alternating quarterwave GaAs (high index) and AlAs (low index) grown latticematched to an offcut monocrystalline germanium substrate. The ideal total thickness of the heterostructure is 6,857.6 nm, with individual layer thicknesses of 77.6 and 91.9 nm for the GaAs and AlAs, respectively, yielding a nominal peak reflectivity at 1,064 nm, as with our previous optomechanics experiments^{47}. With this design, the germanium substrate enables the use of a highselectivity gasphase etching procedure, based on the noblegas halide XeF_{2}, to rapidly and selectively undercut the underlying germanium substrate. Thus, we realize a freestanding epitaxial Bragg mirror via a simple and fastturnaround fabrication procedure. The details of both the epitaxial material design and microfabrication procedure are covered in ref. 50.
Measurement technique
To characterize the frequency response of our microresonators, we utilize a custombuilt optical fibre interferometer featuring a continuous flow ^{4}He cryostat as the sample chamber^{51}. Highsensitivity displacement resolution is achieved in this system via optical homodyne interferometry. Cryogenic testing of these devices is necessitated because of the limitations imposed by TED at room temperature. Estimation of the magnitude of TED is possible using the analytical and finite element models developed previously^{26,27,28}, which predict a Qvalue of ∼4,000 for the current DBR composition and thickness at 1.8 MHz and 300 K—consistent with performed measurements. To avoid TED, our cryostat enables interrogation down to 20 K (resulting in an estimated TED limited Q of 9.9×10^{8}); the minimum temperature is currently limited by the large viewport above the sample stage. Additionally, this system is capable of vacuum levels down to 2.5×10^{−7} mbar at cryogenic temperatures, removing any additional damping induced by fluidic or squeeze film effects^{29,30,31}. The eigenmodes of the resonator are excited by driving a highfrequency (10 MHz) piezo disc soldered to a copper stage in thermal contact with the cold finger. For spectral characterization, the piezo disc is driven with white noise and the resonator frequency response is recorded on a spectrum analyser. For the freeringdown measurements, the decay of a resonantly excited device is recorded in a single shot on a highspeed oscilloscope (see Supplementary Method for further details).
Additional information
How to cite this article: Cole, G. D. et al. Phonontunnelling dissipation in mechanical resonators. Nat. Commun. 2:231 doi: 10.1038/ncomms1212 (2011).
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Acknowledgements
G.D.C. is a recipient of a Marie Curie Fellowship of the European Commission (EC). Additional financial support is provided by the EC (projects MINOS, IQOS, QESSENCE), the Austrian Science Fund (projects START, L426 and SFB FoQuS) and the European Research Council (ERC StG QOM). Microfabrication was carried out at the Zentrum für Mikro und Nanostrukturen (ZMNS) of the Technische Universität Wien, while the heterostructure was grown by Yu Bai at MIT. G.D.C. gratefully acknowledges Stephan Puchegger and Markus Schinnerl for assistance with scanning electron microscopy and focused ion beam milling. I.W.R. acknowledges financial support via the Nanosystems Initiative Munich, K.W. via the Austrian Research Promotion Agency (FFG) and M.R.V. via the FWF Doctoral Programme (CoQuS).
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G.D.C. and I.W.R. designed the experiment (with the use of the free–free design suggested by I.W.R.) and developed the numerical solver. G.D.C. fabricated the microresonators. M.R.V. and G.D.C. designed and constructed the cryogenic opticalfiber interferometer. K.W. and G.D.C. measured the resonator frequency response and extracted the dissipation values. M.A. supervised the research effort. All authors contributed to the writing of the manuscript.
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Supplementary Figures S1S2, Supplementary Methods and Supplementary Reference. (PDF 314 kb)
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Cole, G., WilsonRae, I., Werbach, K. et al. Phonontunnelling dissipation in mechanical resonators. Nat Commun 2, 231 (2011). https://doi.org/10.1038/ncomms1212
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DOI: https://doi.org/10.1038/ncomms1212
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