Application of Computational Fluid Dynamics Analysis for Rotating Machinery—Part II: Labyrinth Seal Analysis

Hirano, Toshio; Guo, Zhiwei; Kirk, R. G.

doi:10.1115/1.1808426

Cited by 96 publications

(44 citation statements)

References 9 publications

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“…The half-Sommerfeld boundary condition can be used to find an approximated solution to fluid flow including cavitation by setting the pressure in the divergent field to 0, and therefore has been employed by many researchers when using CFD analysis [13][14][15]. The pressure distributions from the phase change and halfSommerfeld boundary conditions were in agreement with each other (Fig.…”

Section: Discussionmentioning

confidence: 57%

“…Gao et al [13] used a commercially available CFD code to investigate the static and dynamic characteristics of hydrodynamic and hydrostatic bearings, and a squeeze film damper. The same method was applied to a labyrinth seal to test the stability of a rotor-bearing's seal system [14]. Gertzos et al [15] predicted the performance characteristics of a journal bearing lubricated with a Bingham fluid by means of the CFD method implemented in a commercially available code.…”

Section: Introductionmentioning

confidence: 99%

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Application of Computational Fluid Dynamics and Fluid–Structure Interaction Method to the Lubrication Study of a Rotor–Bearing System

et al. 2010

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Computational methods were used to analyse the elasto-hydrodynamic lubrication of a complex rotorbearing system. The methodology employed computational fluid dynamics (CFD), based on the Navier-Stokes equation and a fluid-structure interaction (FSI) technique. A series of models representing the system were built using the CFD-FSI methodology to investigate the interaction between the lubrication of the fluid film, and elastic dynamics of the rotor and journal bearing. All models followed an assumption of isothermal behaviour. The FSI methodology was implemented by setting nodal forces and displacements to equilibrium at the fluid-structure interface, therefore allowing the lubrication of the fluid and the elastic deformation of structures to be solved simultaneously. This is significantly different to the more common techniques-such as the Reynolds equation method-that use an iterative solution to balance the imposed load and the force resulting from the pressure of the fluid film to within a set tolerance. Predictions using the CFD-FSI method were compared with the results of an experimental study and the predictions from an 'in-house' lubrication code based on the Reynolds equation. The dynamic response of the system was investigated with both rigid and flexible bodies for a range of different bearing materials and dynamic unbalanced loads. Cavitation within the fluid film was represented in the CFD-FSI method using a simplified phase change boundary condition. This allowed the transition between the liquid and vapour phases to be derived from the lubricant's properties as a function of pressure. The combination of CFD and FSI was shown to be a useful tool for the investigation of the hydrodynamic and elasto-hydrodynamic lubrications of a rotor-bearing system. The elastic deformation of the bearing and dynamic unbalanced loading of the rotor had significant effects on the position of its locus.

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Section: Discussionmentioning

confidence: 57%

Section: Introductionmentioning

confidence: 99%

Application of Computational Fluid Dynamics and Fluid–Structure Interaction Method to the Lubrication Study of a Rotor–Bearing System

et al. 2010

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“…4 that the present 3D model differs by about 6% compared to 2D CFD model [11], but is closer to the test data [6]. A detailed grid sensitivity analysis, similar to that of reported in Hirano et al [24] is carried out to ensure the spatial accuracy of the solver. Accordingly, the number of divisions along the longitudinal and circumferential direction is arrived first followed by the lateral direction.…”

Section: Cfd Modelmentioning

confidence: 88%

Influence of combined radial location and growth on the leakage performance of a rotating labyrinth gas turbine seal

2015

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Leakage characteristics, influenced by centrifugal and thermal radial growth are determined computationally for a generic rotating labyrinth seal used in the gas turbine secondary air system. Three seal locations, namely, R25, R50 and R75 are represented by means of varying the rotor radius mimicking different radial positions of the seal from the shaft axis. The combined influence of seal location and its radial (Centrifugal and thermal) growth on the leakage performance is investigated for a wide-ranging speeds from 1000 to 3000 rad/s, temperatures ranging from 200 to 450 o C and pressure ratios varying from 1.1 to 2.5, for a chosen initial clearance of 500 micron. A comparison of the effect of rotation and temperature gradient among different rotors shows that the radial growth and leakage flow rates significantly vary with the increasing radius.

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“…Attention has been given to fluidinduced force for the improvement of turbine operating parameters. In the past years, many studies [1][2][3][4][5][6] used CFD techniques to simulate the flow behavior in seals. Many factors, such as turbulent flow, boundary condition, and temperature variation, among others, cannot be considered accurately.…”

Section: Introductionmentioning

confidence: 99%

Experimental identification of fluid-induced force in labyrinth seals

et al. 2011

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The seal force is an important factor in turbomachineries. Therefore, the current paper puts forward an expanded seal force identification model. A seal test rig consisting of several sets of seals was prepared. Using the double-plane unbalance force identification theory in rotordynamics, the distributed seal force in the cylinder became equivalent to two selected planes. Considering the complex cylinder vibration with increasing rotating speed and inlet pressure, the cylinder was regarded as a vibration system with 4 degrees of freedom.The 4×4 impedance matrix was tested at the two selected planes using a shaker in two orthogonal directions. The equivalent seal force can be obtained by multiplying the impedance matrix with the measured change in the cylinder vibration. In the seal rig, tests were performed on the influence of inlet pressure, rotating speed, eccentricity ratio, rotor vibration, and clearance. The seal force increases almost linearly with the increasing inlet pressure, eccentricity ratio, and vibration amplitude. Furthermore, the seal force is strongly sensitive to the change in clearance between the cylinder and the rotating rotor. The phase difference between the seal force and the vibration influences the work done. If the phase difference is nearly 90°, then the work is at maximum. Moreover, the seal force applies positive force on the cylinder and negative force on the rotor.

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Application of Computational Fluid Dynamics Analysis for Rotating Machinery—Part II: Labyrinth Seal Analysis

Cited by 96 publications

References 9 publications

Application of Computational Fluid Dynamics and Fluid–Structure Interaction Method to the Lubrication Study of a Rotor–Bearing System

Application of Computational Fluid Dynamics and Fluid–Structure Interaction Method to the Lubrication Study of a Rotor–Bearing System

Influence of combined radial location and growth on the leakage performance of a rotating labyrinth gas turbine seal

Experimental identification of fluid-induced force in labyrinth seals

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