Magnetorheological plastomers (MRPs) are composed of a soft polymer matrix, carbonyl iron powder (CIP) and magnetic and nonmagnetic particles. They have the potential to bring significant benefits to multiple industries and become the future of MRP dampers. MRPs are applied in the fields of damping, sensing, and medical devices. Compared with other magnetorheological (MR) materials, MRPs have better magnetisation and sedimentation control. The advantages of MRPs include their higher stability, movability under magnetic fields, lower sedimentation, higher MR effects and higher magnetisation capabilities. An integrated model of computational fluid dynamics (CFD) and finite element analysis (FEA) was used to investigate the dynamic characteristics and controllable damping force of MRP dampers. CIP MRP (CIP-MRP60), hollow glass powder MRP (HGP-MRP60) and MR polymer gel (MRPG60) were used in the analysis. This research considered two different models to simulate the MRP and MRPG dampers. Model 1 simulated a short-stroke MRP damper for the first time, using MRP60 as the carrier fluid. Within this model, there were three distinct regions in the annular shear gap between the piston head and the cylinder. In the first zone, the boundary moved in the opposite direction to the fluid, while in the second zone, the annular shear gap between the cylinder surface and the surface was stationary, and the fluid moved in the opposite direction, resembling a parallel plate model. An initial model was developed to investigate the flow of CIP-MRP60 into the MRP dampers and validate it against experimental results of the MR damper. For these fluids, the relationship between the magnetic flux density (T) and the magnetic field intensity (kA/m) was first developed. The yield stress (kPa) was calculated as a function of magnetic flux density. The relationship between the shear stress and strain rate was developed using the Herschel–Bulkley model, and the damping force was calculated using CFD. Model 2 considered a long-stroke MR damper geometry, and for the first time, it simulated the parallel plate model for the MRP damper using MRP60 as the carrier fluid. The primary innovation of this model was the justification of optimal annular shear gap between the piston head and the moving piston bobbin head. As a result, the fluid moved in the opposite direction to the piston head and piston bobbin head. Both surfaces were operating at their maximum piston velocity, a configuration not documented in existing literature. This study was conducted to numerically investigate the performance of MRP dampers with different annular shear gap sizes. The focus of the analysis was on MRP60 flow behaviour in the annular shear gap region, where the induced magnetic field generated a range of dynamic damping forces depending on the size of the annular shear gap. The numerical simulation involved integrating an FEA to examine the magnetic field in the annular shear gap region with a CFD analysis to simulate the damping characteristics of the MRP damper. This research identified the optimal annular shear gap for MRP damper, a finding that had not been previously documented in the literature for these types of carrier fluid based dampers. This study also included a numerical analysis of the performance of MRP dampers and MRPG dampers utilizing different MRPs (CIP-MRP60, HGP-MRP60, and MRPG60) for the first time. The significance of this study was to conduct a characteristics analysis of the MRP damper and MRPG damper using CIP-MRP60, HGP-MRP60, and MRPG60 as carrier fluids. The results of the FEA showed that as the size of the annular shear gap increased, the magnetic flux density and yield stress decreased. The damping force increased with increasing current and frequency of piston. However, in general, it decreased with increasing annular shear gap size. For the design conditions used in the analysis, compared with other fluids, CIP-MRP60, with its relatively higher CIP content, viscosity, solvent (acetone), magnetic flux density, and yield stress led to a higher vibration control capacity for the MRP dampers. This research also examined the effects of frequencies, payload variations, and piston head velocities on MRP dampers. Frequencies of 1 Hz and 3-5 Hz were applied based on the dampers' structure and loading capacity. The damping force demonstrated a negligible change with the change of piston head maximum velocity. However, an increase in piston stroke length resulted in a noticeable increase in the damping force. This research involved simulating and examining different design and material parameters for MRP and MRPG dampers that may potentially be used by industry for the design of future MRP and MRPG dampers.