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failure of shear pin of gear coupling
2

failure of shear pin of gear coupling

failure of shear pin of gear coupling

(OP)
Recently we had shear pin failure usedin gear coupling between motor and speed reducer gear box . two pins are used 180 degrees apart , the pin sheared within five months , Pin material is ST - 37 . pin neck dia is 24 mm. what is the shear load ,shear torque , fatigue stength of the pin ,please suggest . Motor power rating - 400 kw .RPM - 306 , twenty four hours running . atthe time of failure motor load was founf nominal, some beach marks are seen on the fractured surface , may be fatigue failure . how to find the life of shear pin .

RE: failure of shear pin of gear coupling

Predictions require more information than you have supplied and are very affected by detailed circumstances that sometimes show up as empirical factors with wide variations in results. I suggest finding the analysis that was done to design the joint and see what the prediction was and whether there are any differences between those assumptions and what was delivered.

RE: failure of shear pin of gear coupling

(OP)
CHEMICAL COMPOSITION TEST OF THE MATERIAL IS DONE FOUND OK , HARDNESS IS 18-21 HRC.

RE: failure of shear pin of gear coupling

(OP)
PCD of gear coupling is 395 mm , it's a taper shear pin on one side dia is 35 mm and at the other side it is 32 mm . pin was tight inside t he bush, so no question of radial play inside the bush ,but still it failed .

RE: failure of shear pin of gear coupling

Hi

A picture of the inside faces of the pin would be useful, also what are those marks on the pin half on the left of the picture?

Also a picture of the coupling might be good so we can see whether the hole in it as elongated or not.

We need to know what the torque value was during running and whether it's a fluctuating torque or constant.

My guess is this:- the taper pin as elongated the hole that it was inserted in over time, this as allowed slight movement between pin and coupling which creates bending on the pin as well as the shear stress and the pin eventually fails in fatigue due to bending, if you look at that picture the pin is bent.

“Do not worry about your problems with mathematics, I assure you mine are far greater.” Albert Einstein

RE: failure of shear pin of gear coupling

(OP)
I will send you the photographs of inside face of pin as well as that of coupling ,can't get the torque value as the drive system shows only motor load ,which was nominal at that time . as you have written,pin is bent , from where ?
i am also interested in the mathematical part also . please suggest ,regarding shear load , shear torque ,fatigue strength of ST - 37 material also its life cycle ,shall we go for endurance strength or shear stress for the life of pin .

RE: failure of shear pin of gear coupling

(OP)
actually pin is not taper throughout on one side pin dia is 32 mm and at the other side it is 35 mm . regarding marks on left side of pin ,it happened while taking out the pin .since pin was very tight inside bush .

RE: failure of shear pin of gear coupling

Hi 1234910

Without an knowledge of the load or torque fluctuation we cannot predict how long the pin will last for, all we can do is take the maximum torque and show the pin should not fail under this maximum load but this doesn't prevent a fatigue failure and I would have thought that somebody would have already done the maximum torque load on the pin at the design stage.

I got the impression that the pin was slightly bent on the photograph, maybe it's how the picture as been taken.

“Do not worry about your problems with mathematics, I assure you mine are far greater.” Albert Einstein

RE: failure of shear pin of gear coupling

(OP)
Motor torque = 9550x KW X SF /RPM
= 9550 X 400 X 1.5 /306
= 18725 Nm

Since Max Torque = 110 % of mean torque ( as set from elect side )
SO MAX torque - 1.1 x 18725
- 20597.5 Nm

Shear load on pin = T X 2/D
= 20597.5 X2X/.395 Since PCD of gear coupling = 395 mm
= 104291.13 N
= 104.29113 KN
ie , design load of pin = 104.29113 KN

BREAKING LOAD OF PIN - stress x araa of notch , now this stress we shall take endurance stress of shear stress of the material ST -37
- DO SUGGEST

RE: failure of shear pin of gear coupling

(OP)
if we take endurance strength of material for ST -37 material ,it is = 222 N/ sqmm .
Than breaking load on pin = stress x notch area
= 222 x 3.14 /4 x 24 x 24 since notch dia is 24 mm
= 81388.8 N
=81.3888 KN

and design load is =104.29113 KN
SO 81388.8/104291.13 X100 = 78.04%

IE, PIN CAN CARRY 78.04 % of design load before failure .
is it ok , please check ,or something to be added .
next how to find life of shear pin ( no of cycles before failure ) . and its fatigue strength .using Goodsman equation or using SN curve. please help .

RE: failure of shear pin of gear coupling

I agree with others that the pin appears to have bent. You might also consider that there was some bending stress produced on the pin due to slight misalignment of the inner/outer bores at installation.

Were the coupling pin bores match machined to ensure precise alignment?

RE: failure of shear pin of gear coupling

Hello,
as per the given:
A) loading of one section
Given nominal torque & geometrics etc.: 9550*400*2/(306*0,395*452,4) = 140 N/mm²

B) loadbearing capac. of material (~Eurocode 3 / general)
Given fy with 235 N/mm² & γF to 1,5 & shear: 235/(1,5*sqrt(3)) approx. 90 N/mm²

Concluding:
One section would not suffice to transmit the full load. It is necessary to consider the second pin. The load distribution between these is statically indeterminate, as a rule of thumb (refer parallel keys) we assume an effective influence of 1,5. So:
90*1,5 = 135 N/mm² which is approximately equal to the load. At a give or take something philosophy, one could consider that this is ok.
So it is necessary to go into detail, and here there's not enough database to get a stringent conclusion.
Let's try:
a) Usually, to make up for defects within the material, EC3 & Co lower the loadbearing capac. of material by γM of 1,1
b) you state a possible overloading of 1,1 over the nominal
90*1,5/1,1=123 N/mm² whereas 140*1,1= 154 N/mm².
This is not soundly acceptable.
From your picture:

one could conclude that the shear pin was fixed on one side but was able to move on the other side, which would have induced a bending load (however small) onto the section in question.
Prediction (pls. allow me... winky smile
The fracture shall have started at a single point due to some bending effect and shall have developed as a fatigue crack over a longer period, as the base material is quite ductile. The final crack might show a bending to shear overlay of patterns.

remaining questions
- views on the fracture surfaces
- Check of 400 kW @ 306 rpm and/or info about drive setup & configuration
- derivation of Sf 1,5 in your calc: if factor of safety, where did you take it from and why was this value applied?
- Why was HRC test applied to this low fu / high ductility material? EN 18265 even does not give correlation values at HRC for this range of fu. Perhaps HRB testing is to be preferred?

Regards
R.

RSVP

RE: failure of shear pin of gear coupling

(OP)
Given nominal torque & geometrics etc.: 9550*400*2/(306*0,395*452,4) = 140 N/mm²

What does 452.4 inidcates i nthe above equation ? do suggest and what does 140 N/sqmm indicates ?

Given fy with 235 N/mm² & γF to 1,5 & shear: 235/(1,5*sqrt(3)) approx. 90 N/mm²

give the specific formula ? for th e above equation?

RE: failure of shear pin of gear coupling

(OP)
Since the pin was very tight inside t he bush , with great difficulty it came out ,so freeting ? if their is looseness between the pin and bore than freeting will come into play , if i am not wrong .

RE: failure of shear pin of gear coupling

What exactly was this gear coupling driving for 24 hrs/day?

The thing missing from this discussion for me was the degree and number of cycles of any shock loadings or high stresses.

Remember - More details = better answers
Also: If you get a response it's polite to respond to it.

RE: failure of shear pin of gear coupling

a) 452,4 [mm²] from PI/4*24*24
b) 140 N/mm² is the shear load on one section of 24 mm dia, given nominal loading
c) loadcarrying ability in shear is 1/sqrt(3) smaller than that in tension etc.
d) ? = question mark to indicate request to the OP for input, not verified knowledge (..couldn't be sure, too far away winky smile )
e) It would be very kind to have (some) of these questions from the people around answered, esp. to fatigue issues & the fracture surface pictures. Like some kind of compensation for a good boy, see? winky smile
Thank you in advance

RSVP

RE: failure of shear pin of gear coupling

Is the gearbox and coupling a commercial product?
How is the motor coupling half retained to the shaft.

Is this your type of coupling?
http://omniscientgear.com/wp-content/uploads/2015/...

A 1 inch nominal pin suggests a shaft diameter at least 5 inches diameter

The acceptable methods of fitting large gear type couplings are-
- slip fit coupling hub with keys and setscrews for mild applications
- interference cylindrical fit between coupling hub ID and shaft OD with key.
- key with shallow taper fit which creates an interference fit when the hub is "drawn up" the tapered shaft

RE: failure of shear pin of gear coupling

The pin looks to be pretty beat up after only 5 months of service. What is the driven machine? Does it have a high dynamic torque load?

Walt

RE: failure of shear pin of gear coupling

Is it an optical illusion or did the pin fail at a section that is a smaller diameter than the rest of the pin?

RE: failure of shear pin of gear coupling

Hi 1234910

We really do need more information, any chance of those pictures on the faces of the failed pin and those of the coupling holes?

If this is a coupling you've purchased are you sure it's the correct rating for the job in hand?
Have contacted the gear coupling manufacturer?

Agree with Rolmec on the 90N/mm2 for the allowable shear stress, so the shear stress is exceeded at maximum torque.

Now to do a fatigue analysis you need some data on the load cycling that would cause the pin to fail, you don't appear to have that information however the pin can still fail in fatigue by relative movement between itself and the components it's clamping, thus generating the cyclic loading required.

A rough rule of thumb which avoids fatigue failure is:- if the tensile stress during operation is less than about 40% of the Ultimate tensile strength of the material, then fatigue is not likely to occur.

Why is the pin grooved? It looks to me as the groove would create a stress raiser magnifying the stress in that area which could accelerate the failure.

“Do not worry about your problems with mathematics, I assure you mine are far greater.” Albert Einstein

RE: failure of shear pin of gear coupling

(OP)
rolmec

what does effective influence of 1.5 means , which you have taken in your calculation .

RE: failure of shear pin of gear coupling

the following pls. to be taken a wee little bit winky smile ... even if we are at a serious issue.... in a serious people's forum ...
script runs
R: "Let's make an agreement: I deliver the background to this 1.5 value, and you deliver some pictures of the surfaces!"
1: "Deal!"
R: "Current design standards (e.g. EC3) rule that in order to cover for the statistical variance of loads, calculation model uncertainties and deviations of load magnitude of unfavorably acting variable loads a partial safety factor is to be applied. The value of 1.5 is basically derived from structural standards, but correlates with applicable mechanical design standards (FEM) for the load case Main Loads."
...
script ends
your turn...
I will stop to push now, promise!

RSVP

RE: failure of shear pin of gear coupling

(OP)
oh,yes i was thinking about safety factor only ,i needed clarification, for the word effective influence .

thanks and regards

RE: failure of shear pin of gear coupling

hi

Have you got on pictures on the failed surfaces of the pin which we requested earlier?

“Do not worry about your problems with mathematics, I assure you mine are far greater.” Albert Einstein

RE: failure of shear pin of gear coupling

(OP)
OK

RE: failure of shear pin of gear coupling

80% chance it is because the drive is misaligned with the motor; 20% chance the shear fuse pin is too small for the load, though it might be exactly the right size to prevent destroying the gearbox or the motor.

This assumes the fit of the pin prevents it from bending significantly under the expected load.

I don't have the correct stress analysis references but this is covered under very short beams under shear, which is not a simplified bending load or pure shear, but will also require evaluation of the contact deformation in the bores the pins are in to get a good approximation of the shear load on the pins. Alternatively, a finite element analysis could be used to determine how much radial displacement is tolerable to get to the desired life.

If these pins don't cost much, replacing them at 4 month intervals may be the least expensive approach. Otherwise find a company that does this sort of alignment.

****

Power = T * omega = 400 kW;
omega = (2*pi radians/revolution)*(306 revolutions/minute)*(1 minute/60 seconds); omega = 32 radians/sec
400 kW = 400,000 n-m/second;
T = Power/omega = (400,000 n-m/second)/(32 radians/second) = 14,000 n-m.

Without knowing the radius the pins are at I can't calculate the shear force and therefore not calculate the nominal shear stress. I expect that the loads from misaligment will be much greater than the nominal loads applied by the motor torque.

RE: failure of shear pin of gear coupling

(OP)
PCD OF TWO PINS - 450 MM . SO RADIUS = 450/2 MM .

RE: failure of shear pin of gear coupling

(OP)
3DDAVE
PCD OF TWO PINS - 450 MM . SO RADIUS = 450/2 MM .

RE: failure of shear pin of gear coupling

Based on the .25mm radial flange misalignment shown in your photos, I suspect the fuse pin failed due to a combination of reverse bending cycles and shear. The fuse pins have a close tolerance fit in the flange bushings, the flange faces are closely coupled, the flanges are relatively stiff compared to the fuse pins, so even the modest .25mm radial offset between the flanges would likely produce significant bending stress in the short fuse pin body constrained length.

It would be best to start by correcting the misalignment condition in your drivetrain coupling before considering any other changes.

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