Design of Hydrodynamic Journal Bearings

Design of Hydrodynamic Journal Bearings

Welcome to the last lecture of video course
on Tribology. So, final lecture, we are going to complete bearing design or hydrodynamic
bearing design based on short bearing approximation assuming bearing length is a much shorter
than length diameter of bearing much short term is may be say 0.2 5 times of the diameter.
And most often in the present situation, we prefer short bearings, even then previous
lecture it was pointed out increasing length is going to increase load carrying capacity
and sensitivity of the length is much larger or so stronger; but increasing length has
a some problem like a misalignment more heat decipitation or more heat generation increase
on a temperature wise increase in a coefficient of friction.
So, we need to account this, when we are talking about the design is not only the load carrying
capacity, we need to think from temperature point of view, coefficient of friction point
of view. And again we are always aiming for the miniaturization shorter is the better
that means, smaller size is the better, is from that angle length need to be reduced. So we are continuing with first slide from
the previous lecture you say attitude angle which was shown or which was mentioned in
previous lecture can be given as a 10 inverse of 1 minus epsilon square square root of that
divided by epsilon. By using this relation we can find out attitude angle. And once we
know the extensity and attitude angle we say that, shaft center is fixed is been located
and it shows that, when you try to plot this e verses attitude angle or we say that, epsilon
verses attitude angle what we are going to get, we can change extensity from 0.0 1 to
say 0.9 9 and try to find out what will be attitude angle this is turning out to be one
extensity ratio is very low attitude angle is very large, it is almost 90 degree.
When extensity is very high, attitude angle is much smaller in real, in practical situation
we do not want much smaller attitude angle, that is why from designer point of view keep
extensity ratio up to 0.8 8 or say 0.80 more than that will not be recommended because,
we know there will be some sought of fluctuation in a load, that may increase extensity ratio.
So, from design point of view I prefer 0.8 and minimum value as a 0.5 or 0.4 that means,
this should be the operating zone for the bearing under operation. Reason being lesser
the attitude angle more will be in a stability of operation, that is why whenever there is
attitude angle as much larger extensity is much smaller, we change the bearing, we reduce
the bearing length, we make a necessary grooves in the bearing, so that extensity ratio is
greater than 0.5. And bearing is going to be little more stable
and this is often the case with bearing operating at the high speed applications, because we
know that, as speed is increasing load carrying capacity of the bearing is going to increase;
and if the load carrying capacity of bearing is going to increase, because of the increase
in the speed extensity will decrease, extensity will decrease for the same equilibrium load
and that decrease is in a extensity is going to increase attitude angle which is unfavorable,
that is why many times for high speed operation, we do not go higher with a cylindrical bearings,
we will go higher with a half set bearings, we go higher with elliptical bearings, four
load bearings, we try to disturb the bearing clearance, we try to reduce the bearing clearance
and try to increase stability, increase extensity in those ratio in those zones.
But that is a totally a separate subject for us, we are going to discuss about the bearing
design based on the short bearing approximation and this is a gives an indication try to keep
extensity ratio, we say 0.4 more than 0.4, but lesser than 0.8. If any time bearing extensity
is increasing beyond the 0.8 try to modify the design change the parameter, if it is
a turning out to be lesser than 0.4 try to change the parameter, increase this extensity,
this should be more operating zone for the bearing. Now, we discussed about the load carrying
capacity, we can use a short bearing approximation to the find out that and the addition mention
the bearing length should not be extended, because its that is going to increase the
friction force. Question comes how? That is a what we are
trying to find out how to drive the friction force we know, we have discussed Petroff equation,
but for the bearing we are saying that is inaccurate equation I will demonstrate that,
using the after deriving this friction force formula. Friction force will be depending
on whether there is a metal to metal contact and we know for hydro dynamic bearing there
will not be any metal contact that means there is a only sharing of liquid lubricant, that
sharing can be sharing the stress can be given by using this relation is eta higher the viscosity
higher will be sharing, higher the velocity higher will be the sharing, lesser the film
thickness higher will be the sharing, then comes the pressure gradient and a h by 2.
To find out friction force, naturally we need to integrate this sharing is fix over its
area and that area is R d theta because coordinate into design and extra length and we have only
to demonstrated, that bearing effective bearing they say only half of the bearing, that is
why the integration for the theta will be theta equal to 0 to theta is equal to point.
We again mentioned about the z that at the mid plain we are assuming z is equal to 0
that means extreme will be minus L but, 2 2 plus L by 2, L is a bearing length.
Once we integrate this what we are going to get this expression it is interesting to note
that, F friction force itself depends on the load, this is a W sign 5, whatever the load
applied load that is going to affect the friction force, may be to lesser extent but, it is
going to affect friction force. And we try to see what is this friction force
or relation that is a W sign 5, that can be given in terms of other parameters like eta,
U, L, cube, c, square and we are able to see they are smaller terms are common in this
two, so to simplify it what we can do we can take some common terms and compare this term,
first term with a second term in the second term is negligible for our simple calculation
we can neglect this term, but if it is not negligible, then we need to account slightly
more complex problem. And we talk about the Petroff equation, the Petroff equation can
be derived from this relation itself, if I use epsilon is equal to 0 we are going to
get the Petroff equation same which we have derived in our lecture or earlier lectures.
Now, gives when am using the epsilon equal to 0, that is giving the Petroff equation
but, is the situation there is no extensity or we say that the shaft in that bearing surface
is a center are conceding there is no load carrying capacity of that bearing, how friction
force will be generated? Friction force cannot be generated that means Petroff equation which
is the predicting the friction force, because of that its inaccurate no force, no normal
force, but still there is a friction force that is a that is a that is not a good option
that is why, we say that Petroff equation cannot be used for the bearing design. But
with the modification when we say using an integration of shear stress can give provide
a good results, off course this is based on the short bearing approximation, so it cannot
be 100 percent reliable but, it gives a reliable results.
Now, as I mentioned there number of terms common in this two relations, this expression
we can take common term this common term turn out to be 2 pie eta U L R divided by c and
in bracket also in this square root 1 minus epsilon square. So this will be 1 plus epsilon
square into L e square divided by 16 L R square. So, if I assume 4 R square is equal to d square
that means L by d square term is somewhere here and we are talking about the short bearing
approximation so length maybe equal to 0.25 times of the diameter, so what will turn out
to be this L by d square will turn out to be 0.25 square.
We know extensity, may be 0.8 maximum value we are choosing, so 0.8 square will turn out
to be 0.64, so 0.64 into 0.25 into 0.25 divided by 4 that means 0.25 into 0.25 into 0.25 into
0.64 will turn out to be much lesser than 1, it can be neglected for our simple calculations
for detail analysis this can be incorporated for simple class room calculation it can be
neglected. That is why in our calculation we are going to treat this F or we are going
to write F or estimate F as 2 pie into eta into L into e R U into R divided by c in square
root of 1 minus epsilon square, so this is a simple friction expression we can be utilized
yeah we can utilize this. Now, even though we were discussing of the
friction force from temperature point of view, we want to estimate temperature so that, we
can modify viscosity we can properly estimate the load carrying capacity of bearing as viscosity
is going to affect load and temperature is going to affect viscosity and friction is
going to affect temperature. And this is that common change, so naturally
we required a good approximation do a complete iteration procedure to find out what will
be the final result, prefect combination of temperature viscosity, friction force and
the load that is why we require a flow rate also. If there is a possibility the temperature
or heat generation is there and it is getting convicted and conducted simpler one we say
assume the conduction is 0, that is going to give slightly conservative design to us
but, that is fine for us. And to proceed in that direction we require
what is a flow rate, we discussed earlier if there is a hole arrangement or slot arrangement
we can estimate what will be the flow rate, that is a Q P in addition to that flow generally
occurs because of the velocity, that velocity the circumferential flow can be given by this
relation that is a Q theta flow rate passing from any location, theta location can be given
in this term again when this situation also this term is a almost negligible compared
to this dominating feature or dominating term. So, for our calculation we are going to neglect
this second term we are going to account only for first term and this overall leakage we
say that, when we are finding the flow is coming in may be theta is equal to 0 and theta
pie film thickness is minimum the most of the liquid is a leaked out not most of most
of the whatever the liquid is a some portion of that liquid is a leaked out and remaining
portion is getting circulated. So, we require this leakage rate, that is
going to give us cooling effect because this liquid will be again cool and come back or
whether we can be return back using the pump arrangement and that Q leakage as it is happening,
because of the hydro dynamic action can be given in an other form also we say that instead
of writing Q leakage I can write Q H due to hydro dynamic action and what we say that
here the feed pressure flow due to the feed pressure will be Q P.
Overall may be a combination of Q H plus Q P there will be some sought of a disturbance
when the pressure comes there will be slightly decrease in a Q H or we say overall flow rate
for time being we are neglecting that we are saying the Q H can be calculated by integrating
both the length for two situation what is a the exit condition that Q theta is equal
to pie and what is the entrance condition that is a theta is equal to 0, so theta is
equal to 0 theta is equal to pie that difference is going to give us what will be the leakage
from the bearing Q H coming out of the bearing which is going to give cooling effect.
And in fact, it has been observed 80 to 90 percent heat is been carried away by liquid
lubricant which are going to get leaked from the surface, so this is going to give us a
reliable results reliable in the sense 80 to 90 percent results when we integrate it
we know the U is not depending on z h is not depending on z, so it will be turn out moved
out and the d z will turn out to be complete length that means L by 2 minus minus L by
2 that minus minus will turn out to positive, that is a L by 2 plus L by 2 is equal to 1
that comes out here this will be maximum film thickness or we say that, Q as another that
will be h as a at theta is equal to 0. So this will be c into 1 plus epsilon this
point h will be minimum so that will be c 1 minus epsilon and when we arrange it is
turn out to be Q H is equal to velocity, clearance extensity ratio into length it depends on
all and this is a volume flow rate we can find out there relation here this is the meter
per second meter meter so that will turn out to be meter cube per second.
But if you are interested in mass flow rate, what we are going to do we are going do multiply
with the density, that is generally k g divided by meter cube and meter meter cube will be
cancelled out they will turn out to be k g per unit second, the mass flow rate this is
a important for calculating the temperature raise. So, finding the temperature raise we know
we need to find out what will be the heat generation, that the friction force into velocity
is going to give us what will be the generated heat and that is going to be carried away
by liquid lubricant. Assumption we are saying that there is a no much conduction and most
of the heat is been affected from using the liquid lubricants. So, we required a thermal
equilibrium we say rate of heat generated is equal to rate of heat converted by oil,
heat rate of heat generation can be given it as a F into U, F is given like this 2 eta
U L R into pie divided by c square root of minus epsilon square that is been given over
here and there is a velocity that is can be given as a 2 pie R into N or say that pie
d N is equal to as a m C p as a mass flow rate specific heat into temperature raise
for heat connection and that is going to give us the total temperature raise is equal to
this relation. Now, this temperature raise is going to depend
on viscosity and viscosity is going to depend on the temperature, that is why we are keeping
close loop of temperature and viscosity, then it depends on radius very sensitive temperature
raise is very sensitive towards the temperature radius larger the radius more and more temperature
raise and it depends on the clearance, larger the clearance lesser will be the temperature
raise, this is a overall relation for temperature raise we can calculate using this relations.
And off course, we derived m as a mass flow rate, in previous slide that can be incorporated
over here mass flow rate which was derived in previous slide it was given as row U c
that clearance epsilon into length, substitute rearrange after substitution we are rearranging
this what we are going to get this is a ratio R by c square, that means and this is a related
to the liquid specific heat and density this is a speed and viscosity.
So, larger viscosity larger temperature raise, larger in this ratio R by c larger will be
the temperature raise, larger density which is generally not happen by large this row
and C p will remain constant it is not going to much affect this whatever the temperature
is that if I change the liquid lubricant it is not going to change, because of this product,
but because of viscosity it will change. Now, we can think what we have done we have
derived the relation for load relation for flow, relation for friction, relation for
temperature and flow incorporate the relation of sorry temperature involves the relation
of the flow that is why, we say how to do design first guess extensity ratio extensity
ratio been guess may be 0.5 will be an initial approximation.
We know minimum value 0, maximum value 1 I will take 50 percent of that, 50 percent is
a epsilon ratio, epsilon is equal to 0.5 or extensity ratio as a 0.5 that is a initial
guess we need to go ahead with that. Once we know extensity ratio we can find out the
load we can find out the friction force flow has been already been incorporated in temperature
raise. So we do not have to calculate separate flow rate if there is no flow due to supply
pressure or we say supply pressure is 0 in those situation, otherwise when we are supplying
with a some feed pressure naturally need flow rate need to be counted and separately accounted
for the temperature raise. So, for present case we are calculating the
load for given or estimate extensity ratio, estimate the friction force and temperature
raise. Once we know the temperature raise we need to use lubricant viscosity relation
or we say temperature viscosity relation, to modify to modify the viscosity. Once we
modify again we need to do calculation, we can think about extensity calculation, load
calculation, friction calculation, temperature raise, so it will be continuously iterated
that is why we say repeat steps 1 to 3, so that average viscosity and load are going
to convert after that, even you repeat results are not going to change that is a convergence
it may be 3 step may be 5 step may be 7 step may be 10 step depend on 15 steps depends
on your initial approximation of this. But most of the complicated situation we use
this procedure to provide initial good approximation, however if I use a finite difference method
and start with a some orbiter extensity ratio is going to take long time to convert, but
if I use this kind of short bearing approximation, estimate the results and use those results
as input to the finite difference method, number of calculation will reduce significantly
and overall there will be better we say the overall there will be lot of on that.
So. what we say is we assume some extensity ratio substitute this find out the load carrying
capacity, that is one find out the friction force, then find out the temperature raise.
Once we know the temperature raise delta t modify the viscosity that is a what we have
mentioned there are 3 steps extensity is a guessing, so that is does not require any
calculation as such it is a guess than load calculation friction force calculation temperature
calculation then finally, viscosity calculation. And this viscosity is going to be input to
the load, naturally it requires iterations it requires overall iteration to convert to
one final solution and demonstrate to demonstrate this procedure which is been discussed over
here, let us take one example. What this example means see in this case we
are trying to find out number of bearing parameters, see its determined estimate or calculate minimum
film thickness maximum pressure coefficient of friction we are not done coefficient of
friction, but we know if we are able to estimate friction force and we know the normal load
take that ratio F by W that is going to give me the coefficient of friction.
And this is been, what we say that it is been required to estimate all this, when bearing
is supporting 600 Newton load or the rotational speed of 2000 rpm, rpm rotational speed is
defined, applied load is been defined, shaft diameter is a 40 mm there is a similarly,
bearing dimension also will turn out to be almost 40 mm. Assuming the bearing length
is a 10 mm that the L by D ratio is 0.25 all viscosity is a room temperature is been defined
as a 15 mille Pascal second, beta that is a constant for calculating the viscosity at
any temperature raise is been given as a 0.029. And radial clearance c is been defined as
a 20 micron, it shows clearly the radius of the shaft is 20 micron was 20 mm and clearance
will be 0.1 percent of that that is a 20 micron so we are following that same scheme radial
clearance is a 0.1 percent of radius. Now, some important calculation we say that
U will be utilized again and again, so instead of directly calculating in a formula you separately
calculate what is the Q and that is a calculate a pie d n, we try to find out that is a 4
0.19 meter per second or say for 0.2 meter per second, factor U i Q pie 0.25 divided
by clearance square can be should be calculated separately, because we are going to do iterations
we do not know exactly what will be the extensity ratio, we are going to assume and calculate
W based on that once we calculate W we are going to find out the friction force temperature
raise and viscosity based on that again that means there will be iterations.
That is why we use this calculation separately U L Q pie 0.25 divided by c square this is
not going to be calculated again and again, we can directly use this factor that 8 2 2
7 meter per second directly. Same way for the friction force we use a separate
factor that is a 2 pie R L into R into pie divided by c square again this will not be
calculated again and again, but friction force will be calculated again and again, because
we require iterative scheme we require perfect iterations to evaluate what will be the friction
force. To demonstrate it as I say the first is approximation for me will be extensity
as a 0.5, maximum value is 1, minimum value is 0 ill take 1 plus 0 divided by 2 that it
will turn out to be 0.5, I will be using that as first approximation.
So, when epsilon is 0.5 what we are going to get W as a 1 1 8 lower, I do not have any
other idea we can use some sought of a interpolation, but for that purpose what we required again
the mean value for interpolation we require two values at least first load and then subsequent
second load, so what do we do we know maximum value of extensity 1 this epsilon mid value
0.5 and we are not getting the desirable load load carrying capacity which is 600 Newton
and what we are getting is a 1 1 8 Newton what I will do I will again do 0.5 plus 1
divided by 2, take a mean value that is turning out to be 0.75.
So, extensity 0.75 what we are going to get W as a 562 meter, now I can use some sought
of interpolation to evaluate or I can find out again averaging value 0.75 plus 1 divided
by 2 I can go ahead with that, but that rough approximation says that, generally we do not
recover more than 0.8, so am just taking the value as a 0.8, epsilon value as a 0.8, am
want to find out whether the load capacity is a really exceeding 600 Newton and not.
So extensity 0.8 what we are going to get W as a 900 Newton which is a 50 percent higher
than this naturally we will be we can decrease this take intermediate value of these two
but, we know viscosity which is been used in this calculation is a 15 mille Pascal second
and that is happening at the room temperature, we are not calculated that operating temperature
and viscosity is going to be lesser than this at a operating temperature that is going to
reduce a load carrying capacity. So, for times being we are saying this was
assuming extensity is a 0.8 calculate W calculates friction force, find out the temperature raise
and that is turning out to be 8. 65 degree centigrade.
Now, what is the next step to find out what will be the viscosity for this. Off course,
we have use this relation we say factor one how it is been utilized factor two how it
is been utilized we are not doing this calculation again and again we are simply substituting
the factor, we know epsilon is going to change viscosity is going to change, that is why
except these two we have assuming one constant factor. Similarly, for friction force viscosity
is going to change epsilon is going to change so keep apart from these two factor thing
all other will be constant so, that is what the factor 2, this is required for simple
calculation to reduce efforts. And temperature raise again can be given in this case again
we can find out viscosity sorry speed is a constant 4, 5 is a constant R by c is constant
row C p is constant we can take this as the factor 3.
And here nothing is been mentioned, but we are using the word density of the liquid as
a 860 kilo gram meter Q and c P as a 1 c 1 6 0 joule per unit kilo gram per centigrade,
this is been utilized and most often for liquids these are the results for the liquid lubricant
these are the relations or we say that these are the parameters for liquid lubricant. So,
we can substitute we can find out another factor 3 in this case which will be 4 pie
into n into R by c square divided by row c P, that will cannot be remain constant and
after that we can we can keep changing eta and epsilon to find out final temperature
raise. Now, once we know the temperature raise we
can use this to find out what will be the viscosity, what will be the operating viscosity,
that is viscosity is given as this is defined eta in is already known, beta is defined,
delta t we calculated that is going to give viscosity as 11.7 mille Pascal second, in
our calculation earlier we assume this is a 15 mille Pascal second, so almost 20 to
30 percent change in a viscosity. Now, we need to substitute this value this
viscosity in the load say for epsilon is equal to 0.8 with a modified viscosity what we are
going to get W as a 7 0 3 Newton, earlier we got 900 applied load is a 630 by 50 percent
variation, but after incorporating this viscosity change what we are getting W as a 7 0 3 Newton,
which is still higher than applied load, naturally we need to change extensity we need to decrease
extensity ratio for here for this kind of extensity and viscosity what we are getting
F as a 5.13 Newton calculate temperature raise. So it has reduced from 8.65 percent to 6.75
percent am sorry there are not percent is a 68.65 degree centigrade to 6.75 degree centigrade
it is reduced. Now, at this temperature we will again try
to find out what will be the operating viscosity and that is slightly more, that is turning
out to be 12.3 mille Pascal second, we did calculation for 11.71 Pascal second naturally
this viscosity W will be on a higher side. That is why now it is a time has come to take
an average 0.75 and 0.8 take an average of that turn out to be 0.75 for time being we
are taking extensity ratio as a 0.78. So 0.78 when you calculate this temperature
raise will turn out to be 7 degree centigrade, calculate load at this is turning out to be
fortunately it is turning out to be 599.1 Newton very close, we know we have done approximation
if you want we can keep slightly more load we can increase this 0.78 from 0.7 8 to 0.79
and keep a higher load or depends what we want. In this case, friction force is almost
a same temperature raise is also almost coming to the 0.7 degree centigrade, viscosity operating
viscosity is turning out to be 12.2 mille Pascal second this is a fine design for me.
Or we say if you want to go for the finite difference method this design is going to
give reliable results or we assume that load carrying capacity estimated by short bearing
will be slightly higher, then we can think about 0.7 also 0.79 also which will give roughly
may be say around 640 Newton load capacity applied load is on a 600 we say that is fine
for us we can go ahead, so this is a word we say the how we do calculation.
Next comes how to find out attitude angle we are following the short bearing approximation
we have calculated epsilon as a 0.78 substitute this value find out attitude angle and attitude
angle is turning out to be 302.2 degree that is fine say extensity 0.78 attitude angle
32.2 degree. So this is all about, but problem what we have asked in question find out minimum
film thickness? Find out maximum pressure? Find the coefficient of friction? And we are
not discussed those things, till now this is a first step locate the shaft, find out
extensity and attitude angle and after that do remaining calculations. So, this is we
have completed we have converged to the final results extensity 0.7 8 attitude angle 32.2
degree now time has come to find out the minimum film thickness. We know clearance film thickness can be determined
based on epsilon as a c minus in bracket 1 minus epsilon, substitute this value 20 micron
is a radial clearance 0.78 is a epsilon value is turning out to be 4 .4 microns. Question
comes whether we have done everything right? We are talking about hydro dynamic lubrication
and we know hydro dynamic lubrication we need to will be valid for the specific film thickness
by enlarge more than 5. If surface softness of shaft and bearing surfaces are given to
us or provided to us, we can find out this is specific film thickness using this relation,
that will be ratio of minimum film thickness to the composite self surface softness.
Now, if I assume roughness of the shaft is a 0.4 micron may be on higher side and bearing
may be even 0.6 microns, take a composite one and find out what will be the composite
surface softness if this ratio is turning out to be more than five is say hydro dynamic
lubrication is fine bearing design is as per the hydro dynamic lubrication there is no
problem. If that is not the case then we can think
about adding hydro static lubrication, we can supply pressure that is going to reduce
temperature and that is going to reduce film thickness or sorry reduce extensity when epsilon
is decreased naturally h main is going to increase. So, that way feed pressure is going
to increase film thickness is going to bring is going to bring you say mixed lubrication
domain to hydro dynamic domain so we can do calculation when we do calculation we find
out whether everything is fine and not if it is not then we should use some sought of
pressure to supply liquid to cooler liquid to cool the liquid lubricant can reduce the
temperature make into a factor viscosity more than what is been estimated and.
So this is a film thickness then next comes a maximum pressure, how to find our maximum
pressure this is a short bearing approximation, we know maximum pressure will occur when z
is equal to 0 that is condition which we are used to derive this relation the mid plain
d P by d z will be equal to 0. Now, we have used z equal to 0, but we need
to find out at which angular position maximum pressure is going to be there or maximum pressure
will be generated and pressure profile what will be location of maximum pressure, that
mean theta o max theta o, because of short bearing or we say theta 0 as a we are using
a short bearing approximation. So start with the pressure relation first you say that this
is a pressure relation we say that maximum pressure will occur at z equal to 0, substitute
this, rearrange this and after that in h differentiate with the respective theta. After differentiating
with respective theta equate to 0 that is going to give us that is going to give us
theta for maximum pressure once we know substitute those value over here and find out maximum
pressure. In our case, this been done and we find this
location or maximum pressure theta 0 max depends only on extensity ratio that is a what is
shown over here, it is a 1 minus in square root of 1 plus 24 epsilon square divided by
4 pie. Now we know this will be always greater than 1, that means theta is going to be greater
than 90 degree this is going to be negative. Now epsilon can be 0.1, 0.2, 0.3, 0.4, 0.5,
0.6, 0.7, 0.8 whatever you take this will be negative, if this is a negative our value
will turn out to be negative sorry this will be more than 1 and if it is more than 1 minus
more than 1 naturally will be negative that is why the theta will be always greater than
90 degree. In present case, this is turning out to be
105.43 degree and this is a different than theta is equal to pie, this is difference
that theta is equal to pie that means location of minimum film thickness is different than
location of maximum pressure. Otherwise in many books there is been confuse have been
treated the maximum pressure location and minimum film thickness location are the same
it is not, there locations are different. Now, based on then we substitute this value
theta o max in this expression what we are going to get maximum pressure as 7.24 bar
not very high value is well within permissible limit mega Pascal it is only 0.724 mega Pascal
its not very big, this is a big quantity or larger any material can be used any material
can be used in this situation. Now finally, comes the coefficient of friction
we needed to find out coefficient of friction, we know what is the friction force, we know
what is the applied normal load, take a ratio I have divided the W that is what is going
to get, we are going to get that is a 0.0086, this is very low coefficient of friction 0.0086
almost negligible pressure that is why the hydro dynamic bearings are most popular, whenever
we require good good damping local self friction 0 wear hydro dynamic bearings are on the top
place. Now, what we can do to find out if length
is doubled what is going to happen with this parameters, just now of a present case we
took length is a 0.25 times of the diameter, but if we are going to increase this length,
we say doubled the length instead of 10 mm we can think about 20 mm what is going to
happen. That is shown over here, the same data which
we defined the same viscosity, same load, same speed, same everything right. Now only
the variation is bearing length instead of 10 mm we are considering as a 20 mm, if we
do that, again we need to assume as a first step what is the extensity ratio we need to
guess as I mentioned earlier for me simple case is summation of 1 and 0 divided by 2
that is an average value at the first step and that is epsilon giving as me as a 0.5
this is turning out to be 943 Newton. Now, I can take a again average 0.5 plus 0
divided by 2 that is a epsilon as a 0.25, but we feel epsilon lesser than 0.4 should
not be recommended for in this case, we have recommended a 0.45 minimum value, it should
not be lesser than that. However, we need to change the design. So epsilon if I assume
the 0.45, we can find out the load as a 700 40 Newton, what is a more than 600 we can
reduce it further, but we what we want to do that calculation we know this 741 is at
that 15 mille Pascal second viscosity and if we account the temperature raise this is
will be this will be lesser than that any b if viscosity will be 12 mille Pascal second
or 30 mille Pascal second so this will be reduced.
So, for time being we can assume the extensity of initial approximation as a 0.45 calculate
the friction force and friction force calculation gives the result as a 8.84 Newton, based on
that we can find out the temperature raise, that is turning out to be 10.33 degree centigrade.
Based on this we will modify the viscosity this is a 15 mille Pascal second temperature
raise is 10.33 degree centigrade and beta is given to us in example or we say in a question
so based on that, what we can find out the viscosity that is turning out to be 11.1 mille
Pascal second, we substitute this value to find out what will be the load carrying capacity.
Now, with this viscosity extensity 0.45 load turn out to be 548 Newton which is a lower
than applied load, I can change viscosity or I can change extensity immediately here.
Other one is that calculate again the friction force recalculate temperature raise re calculate
viscosity and again see whether that is going to increase this load carrying capacity reaching
to the final value which we require, if it a case you say that we do the calculation,
now find the friction force evaluate temperature raise based on that find out the viscosity
that is a instead of 11.1. Now is turning out to be 11.9 mille Pascal second substitute
W is turning out to be 588 Newton, again we can do calculation, but we know this extensity
is not going to increase to 600. I can think about this extensity may be say
0.46 and find 4 6 also can give me some result which is slightly more than that, now it is
my choice whether I go for slightly higher value or convergent you say the 588 is a value
within 5 percent of the load I can converge it or we can think about slightly more than
that so when we are talking about the epsilon as a 0.46 and the load carrying capacity is
a 606 Newton, F is a 6.94 Newton. So, I can find out, I can close this example
with extensity as a 0.46 or extensity of 0.45 both the options are open to me this is giving
me high load carrying capacity, that is giving slightly lower load carrying capacity. So
from conservative point of view I can choose this or for the continuity we say no we do
not require too many iterations then iteration is itself is giving a reasonable good results
choose those results. So, depends on the whether we have freezing
0.46 or 0.45 we can find out attitude angle and attitude angle for 0.45 is turning out
to be 57.3 degree, which is a higher value we can increase this we can change the bearing
length, we can reduce the bearing length, we can change the parameters so that extensity
is coming out to be 0.7, 0.6, 0.7, 0.8 that will be the more desirable level, that is
a giving indication bearing length increasing from 10 mm to 20 mm is not full filling the
purpose extensity ratio is going down its more like we have a capabilities and but,
we are not doing our best we are not giving our best performance.
So, bearing have a lot of capabilities but, because of the larger length bearing is not
able to give the best, which is not desirable first thing is a increasing a going for a
larger bearing length naturally cost of the manufacturing is going to be increased, cost
of the material is going to increase, in addition there will be some sought of the some sought
of misalignment in addition there will be friction force I use the word there will be
additional friction force, but we need to check it we say that for a this if I assume
0.45 as a freezing point calculate what will be the maximum pressure.
For that purpose we require theta o max or theta 0 max and that is turning out to be
110 degree 110 degree in this case, that is going to give me value of something like a
P max or the 13 bar or 1 point here mega Pascal, if you remember the length was 10 mm this
pressure maximum pressure was only 0.7 mega Pascal.
So, what we are doing increasing the bearing length maximum pressure is been increased
to 1.3 mega Pascal, one way it is a negative side another way is that bearing material
mostly they are able to sustain more than 5 mega Pascal, so why to worry about 1.3 mega
Pascal let it be like that, if bearing length is giving all other advantages we should go
ahead with a larger length, but temperature from coefficient of friction point of view,
say that coefficient of friction in this situation, because friction force is a 7 Newton in this
case divided by 600 is going to give us a result as 0.0117 coefficient of friction is
a 0.0117 while in earlier example this coefficient of friction was a lesser than this 0.0086.
So, increasing length is not full filling lot of purposes, first extensity is going
down lesser than, we say that 0.5 may be recommended fine, but that is increasing maximum pressure
larger length is giving lesser pressure compared to sorry smaller length is giving larger pressure,
smaller pressure compared to larger length which is a quite reverse. While coefficient
of friction for the smaller length is lesser than larger length, naturally I will prefer
lesser length smaller length for the bearing it rest it is says a space, say the cost gives
optimum performance. And that is what we gain from a studying lubrication
mechanism understanding tribology. Otherwise, if somebody says the load carrying capacity
is go ahead with that maximum length that is a wrong, here lesser length, smaller length
is giving more benefits lesser, maximum pressure, lesser coefficient of friction, lesser space,
lesser cost, so that is essential for us or we say that that is going to give us overall
economics. So, with this am trying to close the course
I hope you understood the course and in future you will be able to say lot of cost incorporating
tribological principles, tribological guidelines thank you, thank you for your attention.

7 thoughts on “Design of Hydrodynamic Journal Bearings

  1. Why can't we increase radial clearance about 30 microns, by keeping the axial length of bearing constant and we have the film thickness of 5microns as well?

Leave a Reply

Your email address will not be published. Required fields are marked *