Fluid bearing

Hydrodynamic (HD) lubrication, also known as fluid-film lubrication has essential elements:

1. A lubricant, which must be a viscous fluid.
2. Hydrodynamic flow behavior of fluid between bearing and journal.
3. The surfaces between which the fluid films move must be convergent.

Hydrodynamic (full film) lubrication is obtained when two mating surfaces are completely separated by a cohesive film of lubricant.

The thickness of the film thus exceeds the combined roughness of the surfaces. The coefficient of friction is lower than with boundary-layer lubrication. Hydrodynamic lubrication prevents wear in moving parts, and metal to metal contact is prevented.

Hydrodynamic lubrication requires thin, converging fluid films. These fluids can be liquid or gas, so long as they exhibit viscosity. In computer fan and spinning device, like a hard disk drive, heads are supported by hydrodynamic lubrication in which the fluid film is the atmosphere.

The scale of these films is on the order of micrometers. Their convergence creates pressures normal to the surfaces they contact, forcing them apart.

Miba Hydrodynamic Tilting Pad Journal Bearing

Three types of bearings include:

• Self-acting: Film exists due to relative motion. e.g. spiral groove bearings.
• Squeeze film: Film exists due to relative normal motion.
• Externally-pressurized: Film exists due to external pressurization.

Conceptually the bearings can be thought of as two major geometric classes: bearing-journal (anti-friction), and plane-slider (friction).

The Reynolds equations can be used to derive the governing principles for the fluids. Note that when gases are used, their derivation is much more involved.

The thin films can be thought to have pressure and viscous forces acting on them. Because there is a difference in velocity there will be a difference in the surface traction vectors. Because of mass conservation we can also assume an increase in pressure, making the body forces different.

• Hydrodynamic lubrication – characteristics:
  1. Fluid film at the point of minimum thickness decreases in thickness as the load increases
  2. Pressure within the fluid mass increases as the film thickness decreases due to load
  3. Pressure within the fluid mass is greatest at some point approaching minimum clearance and lowest at the point of maximum clearance (due to divergence)
  4. Viscosity increases as pressure increases (more resistance to shear)
  5. Film thickness at the point of minimum clearance increases with the use of more viscous fluids
  6. With same load, the pressure increases as the viscosity of fluid increases
  7. With a given load and fluid, the thickness of the film will increase as speed is increased
  8. Fluid friction increases as the viscosity of the lubricant becomes greater
• Hydrodynamic condition – Fluid velocity:
  1. Fluid velocity depends on velocity of the journal or rider
  2. Increase in relative velocity tends towards a decrease in eccentricity of journal bearing centers
  3. This is accompanied by greater minimum film thickness
• Hydrodynamic condition – load:
  1. Increase in load decreases minimum film thickness
  2. Also increases pressure within the film mass to provide a counteracting force
  3. Pressure acts in all directions, hence it tends to squeeze the oil out of the ends of the bearing
  4. Increase in pressure increases fluid viscosity

Bearing characteristic number: Since viscosity, velocity, and load determine the characteristics of a hydrodynamic condition, a bearing characteristic number was developed based on the effects of these on film thickness.

Increase in velocity increases min. film thickness

Increase in viscosity increases min. film thickness

Increase in load decreases min. film thickness

Therefore,

Viscosity × velocity/unit load = a dimensionless number = C

C is known as the bearing characteristic number.

The value of C, to some extent, gives an indication of whether there will be hydrodynamic lubrication or not

• Bearings must maintain pressure to prevent wear and hydrostatic types may be completely immobile when depressurised.
• Overall power consumption is typically higher compared to ball bearings.
• Power consumption and stiffness or damping greatly vary with temperature, which complicates the design and operation of a fluid bearing in wide temperature range situations.
• Many types of fluid bearings can catastrophically seize under shock situations or unexpected loss of supply pressure. Ball bearings deteriorate more gradually and provide acoustic symptoms.
• Like cage frequency vibration in a ball bearing, the half frequency whirl is a bearing instability that generates eccentric precession which can lead to poor performance and reduced life.
• Fluid leakage; keeping fluid in the bearing can be a challenge for liquid types, vacuum recovery and filtration can be needed in some situations.
• Oil fluid bearings are impractical in environments where oil leakage can be destructive or where maintenance is not economical.
• Fluid bearing "pads" often have to be used in pairs or triples to avoid the bearing tilting and losing the fluid from one side.
• Unlike greaseless mechanical bearings, fluid bearings cannot operate at the extremely low temperatures needed for some specialized scientific research applications.

Foil bearings are a type of fluid dynamic air bearing that were introduced in high speed turbine applications in the 1960s by Garrett AiResearch. They use a gas as the working fluid, usually air, and require no external pressurisation system but need careful design to prevent wear during spin-up and spin-down when the bearing makes physical contact.

Water-lubricated rubber bearings have long cylindrical metal shell that hosts multiple rubber staves separated by axial grooves. The usage of the bearing has three major advantages: (i) pumped water going through the bearing is conveniently used as a lubricant, which reduces pump operation cost; (ii) water flow takes away heat and fine particles through the bearing grooves; and (iii) the natural resilience of rubber gives the bearing good properties for shock and vibration absorption and wear resistance. Water lubricated rubber bearings operate under the condition of mixed-lubrication.[5]

Air bearings used to provide linear and rotational motion

Air bearings on a drill spindle for printed circuit boards

Unlike contact-roller bearings, an air bearing (or air caster) utilises a thin film of pressurized air to provide an exceedingly low friction load-bearing interface between surfaces. The two surfaces don't touch. Being non-contact, air bearings avoid the traditional bearing-related problems of friction, wear, particulates, and lubricant handling, and offer distinct advantages in precision positioning, such as lacking backlash and stiction, as well as in high-speed applications.

The fluid film of the bearing is air that flows through the bearing itself to the bearing surface. The design of the air bearing is such that, although the air constantly escapes from the bearing gap, the pressure between the faces of the bearing is enough to support the working loads. This pressure may be generated externally (aerostatic) or internally (aerodynamic).

Aerodynamic bearings can only be operated in high-speed applications, aerostatic bearings are required for load bearing at low speed. Both types require highly finished surfaces and precise manufacturing.

Air hockey is a game based on an aerostatic bearing which suspends the puck and players' paddles to provide low friction and thus sustain high puck speeds. The bearing uses a flat plane with periodic orifices which deliver air just over ambient pressure. The puck and paddles rest on air.

Michell/Kingsbury fluid dynamic tilting-pad bearings were invented independently and almost simultaneously by both British-born Australian, Anthony George Maldon Michell and American tribologist Albert Kingsbury. Both designs were near-identical except for differences in the approach used for pivoting the pads. Michell mathematically derived the pressure distribution where a span-wise line pivot was placed, allowing the load to act through the point of maximum fluid pressure. The Kingsbury patent lacked this mathematical approach, and the pad's pivot point was placed in the geometric centre of the bearing.[6] Michell's patent (in Britain and Australia) was granted in 1905, while Kingsbury's first patent attempt was 1907. Kingsbury's U.S. patent was eventually granted in 1911 after he demonstrated that he had been working on the concept for many years. As stated by Sydney Walker, a long-time employee of Michell's, the granting of Kingsbury's patent was "a blow which Michell found hard to accept".

The bearing has sectional shoes, or pads on pivots. When the bearing is in operation, the rotating part of the bearing carries fresh oil in to the pad area through viscous drag. Fluid pressure causes the pad to tilt slightly, creating a narrow constriction between the shoe and the other bearing surface. A wedge of pressurised fluid builds behind this constriction, separating the moving parts. The tilt of the pad adaptively changes with bearing load and speed. Various design details ensure continued replenishment of the oil to avoid overheating and pad damage.[7]

Michell/Kingsbury fluid bearings are used in a wider variety of heavy-duty rotating equipment, including in hydroelectric plants to support turbines and generators weighing hundreds of tons. They are also used in very heavy machinery, such as marine propeller shafts.

It is likely the first tilting pad bearing in service was built in 1907 by George Weymoth (Pty) Ltd (under A.G.M. Michell's guidance) for a centrifugal pump at Cohuna on the Murray River, Victoria, Australia, just two years after Michell had published and patented his three-dimensional solution to Reynold's equation. By 1913, the great merits of the tilting-pad bearing had been recognised for marine applications. The first British ship to be fitted out with the bearing was the cross-channel steamboat the Paris, but many naval vessels were similarly equipped during the First World War. The practical results were spectacular – the troublesome thrust block became dramatically smaller and lighter, significantly more efficient, and remarkably free from maintenance troubles. It was estimated that the Royal Navy saved coal to a value of £500,000 in 1918 alone as a result of fitting Michell's tilting-pad bearings.

According to the ASME (see reference link), the first Michell/Kingsbury fluid bearing in the US was installed in the Holtwood Hydroelectric Power Plant (on the Susquehanna River, near Lancaster, Pennsylvania, US) in 1912. The 2.25-tonne bearing supports a water turbine and electric generator with a rotating mass of about 165 tonnes and water turbine pressure adding another 40 tonnes. The bearing has been in nearly continuous service since 1912, with no parts replaced. The ASME reported it was still in service as of 2000. As of 2002, the manufacturer estimated the bearings at Holtwood should have a maintenance-free life of about 1,300 years.

Until now tilting pad bearings play an essential role for rotating equipment like expanders, pumps, gas or steam turbines or compressors. Next to the traditional babbitt bearings which were used since the early 20th century modern manufacturers like Miba use other materials for example Bronze or Copper-Chromium as well to improve the bearings' performance. [8]