radial shaft seals ftl seal technology
TRANSCRIPT
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Freudenberg Group
www.simrit.com
30EN2
525.5
0408Trurnit/BoschDruck,
Landshut
Freudenberg Group
The SimmerringReliability right from the beginning
TheSimm
erring
Basics
forpreventing
damage
ErichPrem
Rol
fVogt
Basics for preventing damage
Y o u r T e c h n o l o g y S p e c i a l i s tY o u r T e c h n o l o g y S p e c i a l i s tY o u r T e c h n o l o g y S p e c i a l i s tY o u r T e c h n o l o g y S p e c i a l i s t
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The Simmerring
Reliability right fromthe beginning
Basics for preventing damage
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1. Reliable sealing
2. Shaft surfacesRequirements and working forms
The SimmerringErich Prem Rolf Vogt
Basics for preventing damage
Reliability right from the beginning
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Freudenberg Simrit GmbH & Co. KG reserves all rights, especially copyright and the registration
of industrial property rights. Please observe that this document contains company secrets and anyreproduction or dissemination to third parties may only occur through us.
Protective charge: 10.00 Euro
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Simrit and the Simmerring A 75 year success story
The Simmerring is a universal sealing
component. Its applications range from
agricultural and construction machinery, to two
and four stroke engines in chain saws and
motorcycles, as well as hydrostatic drives in
machine engineering to washing machines
and wind power plants. Simmerrings have the
combined role of sealing a rotating shaft and
a housing from oil loss and preventing theintrusion of moisture and dirt.
To do this, the sealing ring, lubricant and the
shaft surface must be precisely matched to
each other. Because both lubricants as well
as shaft surfaces come in countless designs,
the interplay of the Simmerring with these
components is determined by a multitude of
Dipl.-Ing. Rolf VogtManager Product DevelopmentIndustry
Erich PremProduct DevelopmentIndustry
parameters. The complex interplay of sealing
component, rotating shaft and lubricant not
only present the engineers and technicians at
Simrit with great challenges, they also present
particular challenges to the user. Many
instances of damage and dysfunction arise
simply due to incorrect or at least improper
handling of the Simmerring during installation.
This book will help to clarify the technical
possibilities of the Simmerring component and
its function in the "tribological system". In this
way, production losses caused by improper
handling or its suboptimal application can beavoided. In the first part, possible causes of
failure will be discussed and detailed examples
of damage will be presented. In the second
part, the requirements placed on the shaft
surface will be looked at in depth and how
the current surface treatment processes are
suited to the interplay with the sealing
component will be shown.
Over 75 years ago, Walther Simmerdeveloped the Simmerring at Freudenberg in
Weinheim on Bergstrasse. Over the last 75
years, the sealing component has been
continuously improved and optimised for new
application areas. The resulting wealth of
experience at Simrit is unique and makes this a
book from the experts.
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1. Reliable sealing
How a Simmerring functions 10
Leakage definition 11 Analysis of leakage causes 13
Damage scenarios 18
Handling and installation 25
Troubleshooting 31
Summary 37
2. Shaft surfaces Requirements and working forms
Shaft surface requirements 40
Surface treatment process 41
Leading test 53
Summary 55
Supplementary literature 56
Contents
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1. Reliable Sealing
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The sealing effect of a Simmerring is based
on a simple yet ingenious principle: Through
an intelligent interplay of geometry, material
and manufacturing process, a component is
created that works like a microscopic pump.
This "micropump" not only transports fl uids or
gases under the sealing edge, it can also
transport contamination particles as well.
It is also capable of delivering microscopically
small leakages back into the space to be
sealed. This phenomenal characteristic is the
reason why even the most varied types of seal
disturbance variables can be compensated
for to a certain extent (depending on the
specifications of the seal disturbance
variables), such as
Irregularities in the shaft topology
Shaft eccentricities
Housing misalignment
Skewed installation in the housing (wobble).
It is exactly this defined leakage that is
necessary for a Simmerring to achieve
sufficient lubrication and thus a long
operating life.
Fig. 2: Active principle of a Simmerring (schematic)
Gas orfluid entry
Meniscus
Sealing edge
Seal gap
Lubricant entry
Conveyance effect
Access of air
Contact pressure Contact width
Gap height
Sealing zone temperature
Fig. 1:Simmerring in thetribological system
Dust lip
Grease fillingShaft surface shear
Lubricant
How a Simmerring functions
Reliable sealing
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Leakage definition: the standard,leakage terms, cause, classificationUsing standard test conditions, the lack of tightness is determined by the amount of the sealed fluid - over andabove any moistness which may occur in normal operating conditions which gets past the sealing edge and canbe collected and measured, when the seal is run for a definite time on a test-rig. This collected and measuredamount of media from the test-rig experiment is defined as the leakage.
A certain amount of leakage is
advantageous for a good long-term
seal but is usually no longer tolerated by
today's users. In practice, it is not always
easy to clearly classify the leakage of a
radial shaft ring. The following defi nitions
should assist:
SealedNo detectable moisture at the seal.
MoistIn the case of normal operating conditions,
a fi lm of moisture present on the sealing
edge area which, however, does not exceed
the back face of the seal.
WetA fi lm of moisture exceeding beyond the
back face with drop formation but not yet
dripping.
Measurable leakageDetectable, small rivulet on the outside of the
seal housing, originating from the back faceof the seal. If radial shaft seals clearly
exhibit leakages (e. g. 1 g/day), these
continue to increase with increasing running
time in approx. 80 % of the cases.
Short-term leakageShort-term fault of the sealing system, e. g.
caused by small dirt particles under the
sealing edge which are removed duringfurther operation (affects approx. 20 % of
leaking radial shaft seals).
Apparent-leakageTemporary leakage that is usually traced
back to over-greasing between sealing lip
and dust lip. For further information, read
DIN 3760 or DIN 3761 respectively as
well as from ISO 6194, in which releaseprocedures in conjunction with leakage
classes are described (supplementary
literature 11).
The cause of measurable leakages can be: Various elongations of seal and housing on
the static side for non-compliance with
tolerances
Material tears, particularly in the sealingedge caused by excessive thermal load
during operation
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Hardening of the elastomer caused by
excessive thermal/mechanical loadand/or incompatibility with the medium
to be sealed
Softening of the elastomer as a result
of swelling from the medium to be
sealed leading to premature wear
of the seal
Corrosion of the shaft underneath the
sealing edge and permanent malfunction
of the sealing system
Failure of the lubricant with dry running
and rapid lip wear as the consequence
Ageing of the pairing elastomer medium
to be sealed
Formation of "oil carbon" in the sealing
edge area which fl oats up resulting
in the malfunctioning of the sealing
systemVibrations in equipment assembly and
shaft, which cannot be followed by the
sealing lip
Permanent ingress of contamination on
the sealing lip from the inside or outside
which results in premature wear to the
sealing lip
Premature wear of the sealing lip through
non-compliance with regulations for thedesign of the running surface on the shaft
(see page 15: The shaft)
Damage to the sealing edge during
transport, handling or installation
These causes are to be analysed and appraised
depending on the running time as early failure,premature failure, failure during the operation
or at the end of the part's sealing lifespan.
Classification of occurring leakagesFor monitoring production parts according
to DIN 3761, the leakage classes according
to table 1 are to be used. Deviating test
conditions are to be agreed upon. In
addition, the so-called zero-leakage with test-
rig tests of 240 h with 12 specimens can be
arranged for release for construction, or for
critical installation locations with special
safety requirements. These zero-leakages can
be subdivided according to the following
criteria:
In the course of normal operating conditions,film of moisture at the sealing edge only
Film of moisture over the sealing edge
area but not passing beyond the back
face; no formation of droplets
Film of moisture passing beyond the back
face and/or formation of droplets, but no
dripping occurs
In tests on assemblies and vehicles, zero-leakage defines that state of the radial shaft
seal during static and dynamic conditions
where the sealed medium does not leak
beyond the outer side of the radial shaft seal.
Table 1:Leakageclasses
Leakage class max. permissible leakage max. permissible leakage per radial shaft seal per 12 radial shaft seals
1 1 g 3 g 2 2 g 6 g
3 3 g 12 g
Leakage definition
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Analysis of leakage causes:Static and dynamic leakageTwo kinds of leakage are distinguished with radial shaft seals: Static leakage, which is possible on the press fit andon the sealing lip, and dynamic leakage, which only occurs on the sealing lip.
Upon examining prematurely failing radial
shaft seals (with < 100 operating hours or an
operational performance < 10,000 km) in
detail, failure can be subdivided in the
following way:
30 % attributable to an improper shaft
preparation method [see chapter shaft
treatment/handling]
30 % attributable to an improperinstallation
10 % attributable to a faulty seal [damage
symptoms DIN 3761, part 5]
15 % attributable to apparent-leakage/
premature leakage
15 % attributable to other causes such as
lubricant incompatibility/excessive
temperatures/vibrations/contaminants
Most failures can be avoided through
corresponding installation training or
consulting with regards to the correct shaft
surface preparation method. It is important thatseal and aggregate manufacturers as well as
users are co-operative and that they proceed
systematically with the fault analysis. It can be
Fig. 3: Possible causes of failure for radial shaft seals
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more difficult to determine the causes of
leakage from seals that have already been inoperation over a longer period of time
(months/years or e. g. > 100,000 km). There
are a number of infl uencing parameters and
whose interplay can affect the medium-term
and long-term sealing effect of a radial shaft
seal. The chart [see Fig. 3, page 13] has
proven itself as a sensible analysis instrument
for determining the cause of damage. Using
this diagram, the causes of failure can be
systematically narrowed down. It is important
to know that there is almost never only one
cause of a leak. The interplay of multiple
factors normally leads to leakage. In approx.
80 % of the cases, the cause of failure can be
directly seen on the seal and the shaft. It is
therefore without a doubt of great advantage
for the seal manufacturer to be able to get allthe relevant information on each failure, but
above all to receive the actual seal and shaft
themselves for damage analysis.
You can find the "technical data analysis" form
sheet at www.simrit.de/Schadensanalyse which
summarises the most important information
required for processing a damage claim.
The following describes the most importantcauses of leakage and the corresponding
corrective measures in more detail:
Static leakage at the press-fitThe housing bore is too rough which is
especially critical in Simmerring B1 seal
designs. Nominal:
Rmax
< 6.3-16 m for B1 design
(metallic outer case)R
max< 10 -25 m for BA design
(rubber coated outer case)
Sharp-edged chamfer area and/or too
steep a chamfer angle on the housing boreSimmerring B1: develops longitudinal
furrows
Simmerring BA: elastomer can be sheared
off
Static leakage at the sealing lipShaft is too rough, possibly with
longitudinal furrows caused by the
insertion of a bearing.
Damage to the sealing lip caused by
sharp-edged chamfer or feathered key
groove on the shaft in the sealing lip area
For radial shaft seals with return pumping
action (single or alternating leading), the
sealing lip can be so greatly released
(already at pressures > 0.3 bar ) so that
it only lies on the helix (with non-ventilated housings)
Shaft diameter is too small and/or the
housing misalignment is too great.
Chamfer at the shaft is too small or too
steep so that the sealing lip can tip over
or turn under and the spring can come
off [compare Fig. 3, page 13]
Comment:In dynamic operation of radial shaft seals,
these imponderables can increase the
leakage.
Dynamic leakage at the sealing lipDynamically caused leakages at the
sealing lip occur much more frequently
than static leakages. Hence the causes
are also more complex.The most important infl uencing
parameters are:
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The shaft
Sharp introduced chamfering, scratches,e. g. caused by a bearing that was drawn
onto the shaft [compare Fig. 31, page 23]
Blow holes in the running track area of the
radial shaft seal (pores with a diameter
< 0.05 mm are permissible)
Too smooth or too rough a shaft surface
which can lead to high seal lip wear
An undefined leading of the shaft [compare
Fig. 63, page 53]
can lead to radial shaft seal failure in a very
short amount of time. The shaft surface
topology in particular must be given complete
attention.
The following roughness values must be
adhered to:
Ra0.2 - 0.8 m
Rz1 - 5 m
Rmax
< 6.3 m
These roughness values ensure minimal
sealing edge wear of the radial seal shaft
independently from the machining method
and normally independent of the operatingconditions. Shaft surfaces created through
plunge-cut grinding very often exhibit helical
structures that can lead to leakages within
just a few rotations of the shaft. Measuring
these damaging helical structures is not
easy. In practice, the "thread method" is a
proven method. But not all structures can be
easily measured using this method. Using
new measuring methods, these surfacestructures can nowadays be precisely
detected and thus the relevant grinding
process parameters can be selectively
modified [Supplementary literature 7, 9, 10].
The lubricantsNot all lubricants can be easily sealed. The
complex makeup of the lubricants, the
interaction of the individual additives with
each other and the unavoidable interactions
with the elastomer of the radial shaft seal
can lead to:
Radial shaft seals being chemically
attacked especially at the sealing edge
(Formation of bubbles and fi ller metal
erosion occurrences or even
depolymerisation).
Lubrication additives being deposited at
the shaft in the immediate vicinity of the
sealing lip, developing into hardenedaccumulations with the result being that
even the slightest axial movements of the
shaft cause excessive seal lip wear.
Oil carbon directly on the sealing edge of
the radial shaft seal due to thermal
overloading of the lubricant, caused for
example by high circumferential shaft
speeds, insuffi cient heat dissipation, poor
lubrication of the sealing edge, incorrectlubricant or seal selection. These deposits
can cause tears in the sealing edge,
which signifi cantly alter the seal itself or
simply blister during operation leaving
holes behind.
Radial shaft seals not being lubricated
suffi ciently despite suffi cient supply of
lubricant and thus wearing faster. This
phenomenon can occur especiallywith synthetic lubricants based on
polyalphaolefi n or polyglycol.
Leakage causes
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Operating conditions and environmental effectsWhen early failure of radial seal rings occurs,
an incorrect seal selection or critical
operating conditions are often responsible for
the malfunction. A few practical examplesshould make this clear.
TemperatureThe temperatures directly at the sealing edge
of a radial shaft seal are often underesti-
mated. Depending on the circumferential
speeds, oil sump temperature, lubricant,
lubricant supply and seal concept, the sealing
edge temperature can be from 20 C to40 C above the oil sump temperature and in
extreme cases even 60 C (!) above the oil
sump temperature.
PressureWhen aggregates are not ventilated, a
pressure build-up in the housing can occur
due to thermal expansion and the continuous
air conveyance of the radial shaft seal("micropump"). The pressure increases the
seal lip contact pressure. The thermal
loading of the elastomer and the lubricant as
well as the mechanical load increase. The
results are an increased seal lip wear and
reduced running times.
ContaminationMany radial shaft seals fail due to
contamination, even if they have survived the
first hours of operation trouble-free. It is not so
much the contamination present in the inner
part of every aggregate (form sand, wear
debris from rotating parts), but rather the
external contamination stirred up in the
proximity of the seal. The particles can bedrawn into the sealing gap, accumulate there
and may eventually end up underneath the
sealing edge. Not only does the wear of the
seal lip and shaft (shaft running-in) increase, it
can cause the seal lip to loosen enough so
that the lubricant can pass through the seal
gap and reach the surrounding area
unhindered.
The radial shaft seal itselfNaturally, the radial shaft seal can also be
Fig. 4:Housing and
shaft design
Edge roundedand polished
Edge rounded
1525
1525
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responsible for the leakages. Assuming
the correct material selection and thecorresponding profile design are correct, it is
almost exclusively inhomogenities on the
sealing edge that cause a leakage.
An important aid is the testing of the sealing
edge footprint on a glass mandrel. The radial
shaft seal is pulled onto a glass mandrel,
which has the nominal diameter of the shaft
and the sealing edges system is tested. If the
footprint of the sealing edge on the glass
mandrel is homogenous and is closed
completely, the possibility of a self-caused
leak by the radial shaft seal itself is quite low.
Such inhomogeneities can be caused by:
An instable manufacturing process
Materials inhomogeneities
(manufacture-related)Agglomerisation of fi llers
Tool contamination
Improper handling after forming (among
others things)
Further features that should not be present
on radial shaft seals are mentioned in from
the DIN 3761, part 7.
Claims are often made for leaking radial
shaft seals on which there are no noticeable
irregularities and which are practically in
a new state. A positive test run in the
laboratory usually confi rms the assumption
that the seal itself is in a faultless state so
that the cause of the failure generally
focuses on two points:
On the shaft or its surface structure. This
can generate leakages very rapidly.
Approx. 30 % of all early failures are
caused by an improper installation
[See pages 38 ff. for more information.]
No damage,pores, scratches
RoughnessRmax
Rz
Ra
Rp
Shaft surface topography:Grinding, finish rolling,machining in hardened material
Leading freedom
Sufficient corrosion
protection
Fig. 5: Shaft design requirements as counter direction point of the Simmerring
Wear-resistance: Abrasion,adhesions, surfacedamage, tribo-oxidation
Precise concentricity
Cost-efficient manufacturing
Utilisation through themedium
Good heat dissipation
Leakage causes
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Damage scenarios: Examples of damageThe damage scenarios show examples of the most important causes of leakage that lead to the failure of theradial shaft seal. With their help, it is possible to narrow down the causes of leakage in each case.
Fig. 6: Design of a Simmerring
Back face
Metal insert
Dust lip
Membrane
Back abutment contact surface
Static part, outside diameter
chamfer
Inner liningFront side
Spring
Spring retaining lip
Front sidecontact surface
Sealing edge
Sealing edge:Pre pressed
Trimmedbi directional helixUni directional helix
The sealing edge must be completely closed.The lead impression must be clean as well
There must not be anyloose or firmly attachedparticles on the sealing
edge
Damage scenarios
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Damage caused by thermal overload
The sealing edge of new Simmerrings has acontact width of approx. 0.3 mm. The gap
height amounts to approx. 1 m. Heat
caused by friction is created in this narrow
gap. Approx. 80 % of this is transferred to
the shaft. If this heat is not well dissipated,
the lubricant "cracks" and/or the elastomeris thermally damaged. The results are oil
carbonisation on the sealing edge and/or
thermally-related tear formation in the
elastomer.
Fig. 9: Oil carbonisation beginning in the sealing edge area
Fig. 12: Advanced oil carbonisation and tear formationon the sealing edge
Fig. 8: Tears in the sealing edge
Fig. 11: Oil carbonisation and tear formation beginningon the sealing edge
Fig. 7: Deposits in the leading area
Fig. 10: Extremely strong, strongly adhesive oil carbon depositson the sealing edge
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Damage due to chemical-physical interplay
Not all lubricants are compatible with the sealmaterials. The base oil has less to do with the
interplay with the elastomers. It is the additives
that have more of an effect. These can attack
the seal material already at 60 80 C. It must
always be observed that the sealing edgetemperature in conjunction with the shearing of
the lubricant under the sealing edge can
significantly accelerate damaging interplay.
Fig. 15: Blister formation through chemical interplay
Fig. 18: Formation of blisters/deposits on the back faceof the radial shaft seal
Fig. 14: Chemical interplay between elastomer and medium as aresult of deposits on the running surface
Fig. 13: Strong chemical filler metal erosion of the sealing edge
Fig. 17: Abrasion/bronze and decomposition products from thelubricant in the sealing edge area
Fig. 16: Strong oil carbon deposits with circumferential groovingin the sealing edge area
Damage scenarios
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Fig. 22: Contamination over the entire sealing edge area
Damage due to contamination
True, radial shaft seals are robust sealing compo-nents and can easily compensate for many
disturbance variables. However, they react very
sensitively to contamination in the sealing edge
area. Even during installation, care must be taken
so that no contaminating particles of any kind are
located on the sealing edge since these canquickly lead to leakages, among other problems.
Depending on the application case, corre-
sponding buffer elements such as dust lips, spring
plates or labyrinth seals must be installed.
Fig. 21: Metallic deposits on the running surface
Fig. 20: Contamination between sealing edge and dust lip,e. g. form sand
Fig. 23: Metal shavings and lint on the dust lip caused duringgreasing of the radial shaft seals
Fig. 24: Contamination particles between sealing lip and dust lip causedby improper storage of the seal
Fig. 19: Excessive seal edge wear with circumferential grooveformation in the running surface
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Damage due to excessive wear
Radial shaft seals wear extensively if there ispartial dry running of the seal, if the housing
inner pressure takes on a value of > 0.3 bar
or if abrasive particles from inside (wear from
gear wheels or worm gears, form sand orsimilar) or from the outside (water, sand, dust
or similar) get under the sealing edge.
Fig. 27: Excessive wear due to poor lubrication
Fig. 29: Excessive wear of the sealing edge caused byexcessive pressure being applied
Fig. 26: Excessive sealing edge wear due to high pressureapplied in conjunction with poor lubrication
Fig. 28: Groove formation as a result of increased pressure
at the aggregate
Fig. 25: Groove formation with significant discolourationof the contact surface air side
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Fig. 32: Sealing edge damage caused by blind installation
over a spline shaft
Fig. 31: Sealing edge damage due to the use ofimproper fitting tools
Fig. 33: Damage to the shaft surface due to
improper handling
Mechanical damage
Radial shaft seals react very sensitively tomechanical damage which occur almost
exclusively during handling and installation.
Sharp edges on shaft or housing chamfers,assembly via grooves and gear teeth and
inadequate fitting tools are first on the list.
Fig. 30: Sealing edge damage caused bysharp-edged grooves
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Case study
Disappointing early failures are frequentlyassociated with "apparent-leakage". What
happens quite often is that the user applies too
much grease to the area between sealing lip
Fig. 34:Excessive greasing can
lead to apparentleakages
Fig. 35:Optimally greasedSimmerring
Fig. 36:Optimal sealing edgeof a Simmerring after1000 operatinghours. The sealingedge is free fromdeposits, cleanlyshouldered and has
running width< 0.5 mm
Damage scenarios
and dust lip. This can, depending on theoperating conditions, lose its consistency in a
very short amount of time and it oils out and
thus causes an apparent leakage.
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Fitting tool
The fi tting tools used must exactly match therespective Simmerring as otherwise there is
the risk of irreparable damage.
The Simmerring should preferably be
pressed into the housing using hydraulic
or pneumatic assembly equipment.
Make sure that:
The Simmerring is not inserted at an
angle
The Simmerring does not become
deformed
The Simmerring does not spring back too
far
The Simmering is precisely fixed in the bore
Fitting notesIf the fitting is performed using a pneumatic or
hydraulic press, the fitting speed of 100 to
500 mm/min for Simmerrings with a
rubberised static part and 1000 mm/min forSimmerrings with a metallic static part must
not be exceeded.
Fig. 43:Fitting over a spline shaft (tongue and groove linking)(also for sharp-edged shaft section)
To minimise the spring back and tangential
deviation of rubberised Simmerrings, it isrecommended that the seal not be fitted in
one press but rather that the seal be allowed
to release completely for approx. 1 s at
approx. 1 mm from the end position and then
softly position the seal.
An inclination of more than 0.5 should be
avoided with standard parts.
Examples:
Da 30 mm a = 0,25 mm
Da 60 mm a = 0,52 mm
Da 100 mm a = 0,87 mm
During the fitting, the sealing lip must not
come into contact with sharp-edged
chamfers, edges, grooves or similar since
early failures are otherwise certain tohappen. Fitting collars must also exhibit no
excessively rough surfaces or scratches.
Fig. 44:
The permitted tangentialdeviation in the housing
depends on the seal typeand the shaft diameter
Handling and installation
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When fi tting an aggregate part with a
pre assembled Simmerring, a centeringbolt should be used to prevent tilting and
thus damage to the sealing lip.
If additional components of the aggregate
are to be pushed over the running
surface, e. g. bearings with a press fi t
and the same nominal diameter, the
diameter of the running surface is to be
reduced by 0.10 mm for shaft diameters
up to 30 mm, 0.2 mm for shaft diameters
from > 30 mm to 150 mm and 0.30 mm
for shaft diameters >150 mm in order to
prevent damage. The functioning of the
Simmerring is not affected by this
reduction.
Since elastomers have a reversible
behaviour, the sealing lips can be easily
stretched during the short installation time.
Replacing SimmerringsThe following information should be
observed:
New Simmerrings must be installed
for a repair or overhaul of an aggregate.
The sealing lip of the new Simmerring
must not be located on the same runninglocation. Measures for this are the
installation of spacer rings, the exchange
of shaft Sleeves or the selection of a
different press-in depth in the bore
[see Fig. 45].
Fig. 45: Original fitting (above) and fittingfor repair of the aggregate (below)
Fitting of Simmerring cassette sealsCassette seals are mainly used when very
heavy dirt accumulation is present. The fitting
procedure as follows should be adhered to:
1. Press the cassette into the housing
(as for a normal Simmerring).
2. Wet the slip ring lightly with oil or
grease, but better with an alcohol-water
mixture.
3. Push the shaft (diameter tolerance h8 or
smaller) with roughness values Rmax
< 10 m and Ra< 1.5 m (turned surfaceis suffi cient) through the slip ring of the
cassette.
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Fig. 46: Proper fitting of the cassette
Fitting tipsSimmerrings with an elastomer press fi t
(BA design) must not be additionally
glued into the housing. However, if the
bore diameter is too great or if there is a
high pressure in the aggregate
(> 0.5 bar), the Simmerring can also be
easily glued (e. g. with Loctite 480).
If a part of the elastomer static part shears
off during the fi tting, the housing chamfershould be checked fi rst (geometry,
dimensions, burr free).
The fi tting force can be greatly reducedby using a lubricant, a wax, or a water-
alcohol mixture which thus prevents
shearing. The water-alcohol mixture has
the advantage that the seal sits very fi rmly
in the bore after the alcohol has
evaporated.
If for whatever reason, the adhesion force
of the Simmerring in the bore is not
suffi cient, it is recommended that a smallgroove be added to the bore housing [see
Fig. 47, page 30].This reliably prevents
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the seal from springing back and can
increase the press-out force by a factor oftwo.
Simmerrings occasionally "wander" out of
the housing bore after fi tting. The reason
can almost always be found in the too
small press-in depth of the Simmerring in
the bore.
Note: The cylindrical static part of the
Simmerring must not be in contact with
the housing chamfer [see Fig. 47].
Simmerrings with a pure metallic static
part should be fi xed with an adhesive
(e. g. Loctite 480) or better with a sealing
compound (e. g. Epple 33 or Loctite 574)
in the bore.
Contaminated radial shaft seals should be
lightly rubbed without fail before fi tting
using a lint-free cloth or cleaned with ablast of air.
Even the smallest of dirt particles like lint
can release the sealing edge enough so
that a leakage is certain right after the
installation.
The application of grease between the
sealing lip and dust lip should not be
done with a brush.
A defi ned greasing on site using a greasemandrel matched to the product is best.
The amount of grease should be less than
40 % (except for compression-loaded
Simmerrings).
Through the grease discharge, so-called
apparent leaks frequently exist since 1 g
of washed out or "bleed" grease can
create up to 35 drops of oil (!).
Fig. 47:The correct press-in depth
Preventing potential errors
It has proven benefi cial to perform aninternal installation audit from time to
time. A support manual was created
which contains the most important
parameters that affect the function and
lists the corresponding remedial action
[see the following chapter for this].
Direction: The Simmerringmust sit deeply enough in thehousing bore
A holding grooveprevents the sealfrom springing back
Not this way please!The cylindrical static part of theSimmerring must not be in contact
with the housing bevel
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The compilation of possible sources of error during the fitting and handling of Simmerrings by the usershould help our customers recognise pitfalls and choose corresponding remedial measures. Please consultour technical support.
Troubleshooting: Sources of errorand recommended remedial actions
Sources of error Possible errorsConsequences for
the sealingfunction
Cause of theproblem
Remedial action
Receipt of goods
Damage to thepackaging
Contamination ofSimmerrings
From reduced lifespanto immediateleakage
Incorrect transportpackaging
Test the parts for conta-mination, visual andsignificant changes,improve handling,optimise packaging
Storage (larger quantities over longer time period)Intermediate storage (consumable quantities, supply for the installation)
Non-compliance withthe storageconditions accordingto DIN 7716
Installation of faultySimmerrings
Reducedlifespan
Non-compliance withthe storagerequirements
Storage conditionsaccording to DIN 7716must absolutely becomplied with
Contamination ofSimmerrings
Installation and use ofcontaminatedSimmerrings
From no influence toimmediate leakageas well as reducedlifespan
Dust, dirt
Clean Simmerringbefore installation usingsuitable cleaning agent(DIN 7716), Openoriginal packaging firstat the installationlocation
Damage of the
Simmerring
Installation of
damaged Simmerrings
Immediate leakage or
reduced lifespan
Premature ageing due
to improper storage
Open the original
packaging first at theinstallation location
Transport (from intermediate storage to installation location)
Damage to thepackaging
Contamination ofSimmerrings
From reduced lifespanto immediate leakage
Improper handling Blocking of andspecial clearanceprocedure for parts indamaged cartons, testfor contamination
Intermediate storage at the installation location (consumable amounts)
Contamination ofSimmerrings
Installation of acontaminatedSimmerring
From no influence toimmediate leakage aswell as reducedlifespan through addedwear caused by dust,dirt
Clean Simmerringbefore installation usingsuitable cleaning agent(DIN 7716)
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Sources of error Possible errors
Consequences
for theSealing function
Cause of theproblem Remedial action
Open storageof pre-greasedSimmerrings
Contamination of thegrease
From no influence toimmediate leakageas well as shortenedlifespan throughadded wear
Caused by dust, dirt fromthe surroundings
Always cover the packagedunit and protect from dustand dirt, only remove therequired consumableamount
UnsuitableStorage containers
Contamination,damage if theSimmerring springsnaps out
From no influence toImmediate leakageas well as shortenedlifespan throughadded wear
Accumulation of dirt andmoisture in the storagecontainer, sharp-edgedcorners
Bottom opening, easy toclean containers with nosharp edges
Preparation of the Simmerring for installation
Improperopening orremoval from thepackaging
Cuts or similardamages on the outerdiameter, snappingout of the spring,installation of theSimmerringwithout spring
From immediateleakage to reducedlifespan
Sharp-edgedor unsuitable tools oropening methods
Suitable packagingand tools, special cautionand instruction of theassembly fitter
Greasing of theSimmerring withcontaminated oil orgrease
Contamination of theSimmerring
From immediateleakage to reducedlifespan throughincreased wear
Dust, dirt Protect the grease containerfrom contamination andkeep closed when not inuse
Unsuitable oil forlubricating the shaft Chemical influenceon the seal material,squeaking (stick-slip)
Reduced lifespanthrough increasedwear
Unfavourable lubrication,no contact oil with theSimmerring material
Discuss oil types withcustomer consultant, neveruse graphite grease
Too much greasebetween sealingedge and dust lip
Grease dischargeduring installation oroperation
Apparent-leakage Incorrect amount ofgrease
Max. amount of grease:Approx. 40 % of thegrease space
Too much grease onthe oil side
Grease dischargedrawsoil leakage with it
Leakage leads tofailure
Incorrect fittinginstructions
No grease on the oil side
No or toolittle grease
Insufficient lubricationof the dust lip,increased dirt entry,rubber abrasion
Reduced lifespanthrough increasedtemperatures in thedust lip area orthrough prematurewear
Incorrect instructions orwrong dosage amount
Position the grease amounton the dust lip
Application of greaseto incorrect area
Insufficient lubricationon the dust lip
Reduced lifespanthrough increasedtemperatures in thedust lip area orthrough prematurewear, apparentleakage
Incorrect instructions orwrong dosage amount.Incorrect greasing unit orincorrect greasingmandrel
Use pregreasedSimmerrings, modify theconstruction of the greaseapplicator
Applicationof the grease
Contamination,chemical influences,damages
From immediateleakage to reducedlongevity
Dirt, dust, applicationtool, cleaning tool, fordamages or sharp edgeson the greasing mandrel
Check for cleanliness,suitable tools.Information and training ofthe fitting technicians
Greasing of aSimmerring withoutgrease chamber
Apparent-leakage None Insufficient/incorrectinformation
Select a different seal type
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Sources of error Possible errors
Consequences
for the sealingfunction
Cause of theproblem Remedial action
Installation: Fitting/mounting fixture, mounting location, fitting technician
Incorrect design ofthe fitting mandrel
Damage to the seal,spring snaps out.Simmerring installedat an angle
From no leakage toimmediate leakage,reduced lifespanthrough unevenwear
Customisation:Simmerring shaft housing fitting mand-rel. Mounting fixtureincorrect
Co-ordinate adjustmentwith Freudenberg, observethe suggestions of theDIN 3761,Simrit catalogue recommen-dation
Contaminated
fitting mandrel
Contamination fo
the Simmerring lea-ding to possible da-mage
Premature failures or
reduced lifespan
Dust and dirt at the
working station
Pay attention to cleanliness,
clean the fitting mandrelregularly
Damagedfitting mandrel
Damage to theSimmerring
From immediateleakage to reducedlifespan
Fitting mandrel not OK Regular checking
Incorrectfitting mandrel
Damage to theSimmerring
From immediateleakage to reducedlifespan
Mix-up/noassignment: Simmer-ring-fitting mandrel
Correct fittinginstructions
Too high a fitting
speed
Spring back and/or
skewed position ofthe Simmerring,Damage to the outerdiameter, snappingout of the spring
Uneven wear,
reduced lifespan,static leakage
Fitting speed/hammer
fitting
Comply with recommended
max. speed
Too high a press-inforce for a fitting tostop
Damage to theSimmerring(bending of the me-tal part)
From immediateleakage to reducedlifespan
Press-in force too high/fitting to stop
Reduce the press-in force/force limit/end stop on the fittingmandrel/do not press-in tostop: Path limitation
Press-in path tooshort/too long
Sealing lip anddust lip running on
incorrect location
From no influence toImmediate failure/
early failures
Fitting mandrel ormounting fixture not OK
Check Simmerring for cor-rect seating/set press-in
pathafterwards
Hammer fitting Damage to theSimmerring andof the installationchamber/snappingout of the spring,skewed position
From immediatefailure to reducedlifespan
Improper fitting In a series production, ahammer fitting should notbe used/in the case of re-pairs with hammer fitting,select a stable seal design
Fitting locationunclean(remove cigarette
ashes), sharpedges/metal chips
Seal or mountingfixture contaminatedor damaged
From immediatefailure to reducedlifespan
Dirt, sharp edges Keep fitting locationclean and free from dama-ge. Qualification/clearly
and simply displayed ins-tructions: Visualisation/sen-sitisation for sealing compo-nents
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Sources of error Possible errors
Consequences
for the sealingfunction
Cause of theproblem Remedial action
Simmerring running location (shaft) on fitting location
Scratched shaft Damage to thesealing lip duringinsertion of the shaft
From immediatefailures toreduced lifespan
Transportation damage/missing shaft protection/improper storage andhandling of the shaft
Check the shaft beforeinstallation/DIN 3761observe/use suitableprotective covers andtransport container/donot store or transport shaftas bulk cargo
Contaminated shaft Damage andcontamination of thesealing lip duringinsertion of the shaft
From immediatefailures toreduced lifespan
Insufficient shaftprotection/unsuitabletransport container/unclean handling
Clean shaft beforeinstallation/use suitableprotective covering andtransport container
Corroded shaft Damage andcontamination of thesealing lip duringinsertion of the shaft
From immediatefailures toreduced lifespan
Insufficient corrosionprotection/humidity toohigh/ storage too long/insufficient-transportcontainer or missingcovering
Check shaft before theinstallation for corrosion/never use a corrodedshaftApply suitable corrosionprotection/reconditioncorroded shafts
Corrosionprotection Chemical reactionwith the Simmerringmaterial or thesealed oil
Reduced lifespan Unsuitable materialcombination or corrosionprotection material
Co-ordinate adjustmentwith Freudenberg/test thecorrosion protectionmaterial for suitabilitywith the Simmerringmaterial in the laboratory
Installation of theshaft, poor slidingon of the Simmerringsealing lip orthe dust lipdiaphragm onto theshaft
Spring snaps out/upending of thediaphragm or dustlip
Reduced lifespan Insufficient lubrication/chamfer of theshaft not OK/SL coveringtoo large/incorrectSimmerring design
Sufficient lubricationfrom Simmerring andshaft/observeFreudenbergrecommendation to theshaft chamfer.Match Simmerringconstruction with thefitting as well as theinstallation room
Blind fitting: Longshafts/heavy shafts/tipping of the shaft
Spring snaps out/upending of thesealing lip or dustlip/skewed positionor damage to theSimmerring
From reducedlifespan toimmediatefailure
Insufficient guidingof the shaft
Match Simmerringconstruction with thefitting as well as theinstallation space/selectsuitable sealing concept
Housing bore
Two-parthousing
Combination withincorrectSimmerring staticpart design
Static leakage UnsuitableStatic part design
One part housing/select outer rubbercoating or partial rubbercoating/sealing lacqueror adhesive areunsuitable here
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Sources of error Possible errors
Consequences
for the sealingfunction
Cause of theproblem Remedial action
Cast housing pores/blow holes/casting sand
From static leakage/increased wear toreduced lifespanthrough casting sand
Casting quality notsufficient/insufficientcleaning
Pores and blow holesmaximum 1/3 of thestatic part width/improvecleaning
Die-cast housing(Al, Mg)
Press fit notsufficient/skewedposition/spring backor wandering out ofthe Simmerring (withouter rubbercoating)
Insecure fitting/reduced lifespan
Housing bore too fine/unsuitable static partdesign
Rz> 10 m and < 25 m/select outer rubber coating
Die-cast housing(Al, Mg)
Electrochemicalcorrosion (formetallic press fit)
Static leakage/damage from metalpart or housing
Voltage potential(quiescence potential)
Suitable factory pairing/select outer rubber coating
Die-cast housing(Al, Mg)
Damage to the borefrommetallic press fit
Static leakage/reduced lifespan/bore scratched (notOK) in the case ofrepair
Unsuitablestatic part design
Select outer rubber coating
Plastic housing Damage to the borefrom metal press fit/influence of thermalexpansion or toosmooth surface
Static leakage/reduces lifespan
Unsuitable materialpairing orstatic part design
Select outer rubber coating
Insert chamfer in thehousing incombinationwith an outer rubbercoating on theSimmerring
Shearing off ofrubber with outerrubber coating/skewed position/springback of theSimmerring
Static leakage Burr formation on thetransition from thechamfer to the bore/chamfer too large ortoo small/Simmerringis out of round
Ensure freedom from burrs/observe recommendation ofthe DIN 3761 with regardsto the chamfer
Housing bore Shearing off ofrubber/Simmerring
Static leakage Chamfer too large Select chamfer = 15 20
Handling of aggregates with seal already installed in the production line
Seal laying open orunprotected
Contamination/hardening of theelastomeric material
From reducedlifespan toimmediateleakage
Dirt and dustin the surroundingareaUV light/ozone
Select suitable covering ofthe seal for protectionagainst damage and foravoiding negative influenceslike ozone or UV light/select
suitable sealing system,which protects itself/carefulfitting/detailed instructions
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Sources of error Possible errors
Consequences
for the sealingfunction
Cause of theproblem Remedial action
Seal laying open orunprotected
Damage From reducedlifespan toImmediate leakage
Mechanical effect ofcomponents, objectsor working processeson the seal/insufficienttransportationprotection for looseparts
Select suitable covering forthe seal for protection againstdamage and for avoidingnegative influences like ozoneor UV light/select suitablesealing system, which protectsitself/careful fitting/detailedinstructions
Corrosion of theshaft or housing Corrosion at thesealing lip runninglocation
Reduced lifespan High humidity/insufficient corrosionprotection
Corrosion protection/covering of the seal/limit humidity
Transport Spring snaps out Reduced lifespan Unsuitabletransportationcontainer/Simmerringcentred on mandrel
Suitable transportationcontainer/perform a check ofthe spring seatingbefore the installation
Fitting Damage to thesealing lip
From reducedlifespan toimmediate leakage
Keyway gearing Use mounting sleeve
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Simmerrings are proven, robust and reliable sealing
components. However, they are subject to a natural amount
of wear due to the interplay in the tribological system.
Determining the cause of leakages is therefore a difficult
issue. Damage scenarios show the most important causes that
lead to failure of the seal and provide the first clues. The actual
cause of the damage can, however, only be determined
through a systematic limitation of the possible damaging
mechanisms in conjunction with an immediate analysis of
shaft, lubricant, and radial shaft seal.
Experience shows that roughly 30 percent of early failurescan be traced back to improper installation. Practical
information for the proper storage, for the corresponding
fitting tools for the design of the shaft and the housing as well
as for the correct greasing of the Simmerrings should help
with the removal of these error sources. Moreover, regularly
performed installation audits and training contribute to
helping to isolate weak areas and permanently prevent them.
Summary
Summary
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2. Shaft surfacesRequirements and working forms
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Shaft surfaces
Freudenberg Simrit GmbH & Co. KG40
Shaft surface requirementsTo be able to ensure trouble-free functioning,
the components in the tribological system
Simmerring lubricant shaft surface must
be optimally matched to each other.
It is not always easy since the processes in
the actual sealing zone are so complex due
to high pressures, temperatures, shearing
forces, infl ow of oxygen and transient
interplay between the seal material and
the lubricant or its additives
[cf. Fig 1, page 10].
The design engineer should thus rely on the
experience that the seal manufacturer can
offer. If the operating conditions are known,
the manufacturer cannot only recommend acorresponding seal, but rather, can also
submit suggestions as to how the shaft
surface should be machined.
The requirements of a shaft or its surface are
only signifi cant at fi rst glance. It should
be burr free
not fall below or exceed the specifi ed
roughness parameters. For ground shaftsit is recommended in accordance with
DIN 3760 or 3761:
Ra0.2 - 0.8 m
Rz1 - 5 m
Rmax
6.3 m
exhibit no damage of any kind, such as
scratches, scoring, pores, corrosion
have suffi cient dimensions, abrasion-
resistance.
For this reason, the shafts should be
hardened for possible inner (casting sand,
residual oil, metal particles, varnish and
outer (water, dust, mud) contamination.
It is also recommended that the shafts be
hardened for pressurised seals and for high
circumferential speeds (> 12 m/s) as well.
Furthermore,
the shaft diameter should be toleranced
to ISO h11
the roundness tolerance IT 8 should
not be exceeded
the lubricant should wet the surface
suffi ciently
the surface should also maintainthe lubricant fi lm under load
(e. g. pressure)
and of increasing importance today,
the machining process should be as
economical as possible.
In order for the shaft to withstand the
technical requirements, the correct
machining method is of great importance.These processes in the order of their
importance are introduced below.
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Surface treatment processesThere is an abundance of possible surface
treatment processes for shafts:
Grinding
Turning
Tangential turning
Roller Burnishing
Peening
Superfinishing/honing
Polishing
Quickpoint grinding
Outer grinding
However, not all of these processes are
suitable in combination with Simmerrings.
The most important are evaluated accordingto the latest thinking:
GrindingShaft surfaces for seals are often groundDecades of experience show that plunge-
cut grinding is a safe and proven process
for creating a functional surface for radial
shaft seals. However, there are early failuresof radial shaft seals again and again
which can be traced back to an improperly
prepared shaft.
One of the main requirements of a ground
surface is the absence of lead. This should
ensure no shaft draw direction in the form
of a thread-like structure is present. This
"conveying structure" can have a negative
effect with the corresponding direction ofrotation on the sealing function of the radial
shaft seal. In practice, the requirement
Fig. 48: Grinding of shafts
for "lead-free" shaft surfaces is, however,
virtually impossible. Even when plungegrinding is performed in accordance with
specifi cations, this does not guarantee
a lead free surface.Important process
parameters like constants and, above
all, revolution speed rates are often not
adhered to or checked, the dressing tool
requirements for the grinding disc (feed rate,
cutting depth, cycle) are not adhered to and
the sparking out time is often not suffi cient.External factors such as machine vibrations,
bearing play etc. can have a negative
infl uence on the surface structures. The main
problem is, however, that the effects of
these process parameter changes or process
fl uctuations are not exactly detectable and
measurable.
Surface treatment processes
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Residual lead can cause leakage.
Although prescribed surface roughness valueshave been adhered to and the shaft surface is
seen to be in a satisfactory condition, it fre-
quently happens that radial shaft seals leak
within a few operating hours.
The reason for this is the microscopically small
lead on the shaft surface. An individual helix
("thread"), independent of pitch, is not
normally harmful to radial shaft seals, due to
its small cross sectional area. The problem is,
however, that the ground surface normally
has several "threads".
Thus, if the ratio between the grinding disk
and the shaft is, for example, 10:1, it is
possible for a 10-start thread structure to be
set up on the shaft surface whose pitch will
correspond precisely to the dressing feed of
the dressing tool. The result is that the fl uidtransport through the threads, corresponding
to the direction of rotation, can exceed the
natural pumping capacity of the seal.
Sparking out time is crucial
The main factor to be aware of when grind-ing surfaces for radial shaft seals is the
sparking out time. Since a thread structure
can never be avoided, irrespective of pro-
cess parameters, it is necessary for the spar-
king out time to be adequately high to elimi-
nate it altogether. Sparking out times of 30
seconds should be regarded as a minimum.
Figure 49, however, illustrates that the sur-
face of a ground shaft will not be homoge-
nous, even with practically perfect process-
ing and the appropriate sparking out time.
To some degree, abrasive grit will press the
surface peaks to one side or will tear out
whole areas.
The greater the resulting damage which arises
in the axial plane on the shaft, the lower will
be the resistance to fl uid fl ow, resulting in in-creased leakage.
Only exact adherence to the process parameterscan make grinding secureIf the prescribed process parameters are
adhered to, then grinding will be a reliable
production process. Minor imperfections in
the surface texture can and must be com-
pensated for by radial shaft seals.The most important process parameters and
their infl uence on the radial shaft seal are
summarised in Table 2.
TurningIn the last few years, the machining of
hardened shafts has been continually
improved. In the meantime, this technology is
integrated in the manufacturing process at
Fig. 49: REM image of a plunge-cut shaft surface. (The sparking out timeamounted to 3 minutes!)
Surface treatment processes
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Influence of the manufacturing parameters for the grinding on the sealing effect
Table 2: Relevant machining guidelines for ground surfaces
Process parameters Consequence Aim Observance
Rotational speed ratioGrinding disc/workingmaterial
Can cause a leading Not in whole numberse.g. 10.5:1
Check during the process
Rotational speed workingmaterial
Rotational speedgrinding disc
Can cause a leading 30 300 rev/min1500 1700 rev/min
Tool and working material mustrotate in counter directions
Dressing traverse speed Influences the slopeof the conveying thread
< 0.1 mm/rotation Dressing should only occur inone direction
Dressing tool Can cause aleading structure
Multi grain diamondSingle grain diamond
Dressing infeed Influences roughnessvalues
approx. 0.02 mm
Sparking out time Influences cross sectionof the conveying thread
Complete sparking out, atleast 30 seconds
Most common causes forlead afflicted surfaces
Infeed depth Can cause leakage >> as Rmax
from theprevious machiningprocess
Grinding disc/granulation
Influences theroughness parametersR
a; R
z; R
max
Example: 60 100;Aluminium oxide60KL8V25 (white)Dimensions 400 x 50 x127
Concentricity of thetools andworking material axis
Creates leading structureon the surface
Concentricity as smallas possible
Surface treatment processes
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many companies for economic reasons. With
only a few exceptions, the sealing area of theshaft is still ground. Since one can create a
directional lead on a shaft, this can be utilised
for use in aggregates where one direction of
operation is used primarily:
Engine
Gearbox input
Gearbox output and differential input
(to a degree)
The "helical lead" on the shaft surface can
thus support the radial shaft seal and pump
the sealed lubricant back into the aggregate.
Many attempts under the most varying
conditions have shown that Simmerrings
on turned shafts function perfectly with the
corresponding direction of rotation. More andmore aggregate manufacturers are thus using
a turned shaft as a counter direction point for
the seal.
Hard turning is economicalThe technical success is supported through
the high effi ciency of the process. There is
Fig. 50: Turning of shafts
signifi cant potential for reducing costs in
comparison to other processes.In comparison to grinding for example, the set-
up costs can be reduced by up to 95 %, the
process times by up to 40 % and the machine
purchase costs by up to 50 %.
Another advantage is that the surface texture
with turned shafts is precisely defined and
markedly homogenous [see Fig. 51].
Matching to the direction of rotation is importantFor many application cases, however, the
direction of rotation is not completely clear or
the rotation can occur in both directions.
The seal manufacturer recommends radial shaft
seals with an alternating leading or radial shaft
seals according to DIN 3760 (without leading)
for such applications. Turned shafts with
corresponding direction of rotation can, intheory, convey sizeable lubricant volumes
underneath the seal on account of their leading
("helical threads") and in dependence on the
operating conditions. If one considers the use
of turned shafts for applications with which the
direction of rotation can vary, the seal must be
capable in all operating conditions of being
able to capture the leaked oil quantities and to
be able to pump them back into the sealedarea, thus opposed to the effect of the leading
of the shaft. Of significant importance here is
that the seal be capable over a longer period
of time of pumping these fluid volumes back
since the surface structure of the shaft normally
shows little wear, i.e. remains in tact for long
periods of time.
The pumping effect of the seal is crucialThe critical factor is thus the pumping action
of the radial shaft seal. This is significantly
Surface treatment processes
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Table 3: Proven manufacturing parameters for the hard-turning of shafts
Comment:Simmerrings function perfectly
on soft-turned shaft surfaces. Experience
however, shows that the turning of soft shaftsoften proves to be more difficult than the
hard machining. Therefore, different cutting
In practice, the following manufacturing parameters are proven:
Feed rate: 0.03 0.10 mm/revolution(in the testing field, even values of > 0.1 mm/revolution were tested positively,but larger values should not be specified without testing)
Cutting speed: 100 220 m/min(very good results and durability are achieved at 200 m/min)
Cutting edge radius: 0.4 1.2 mm(a radius of 0.8 mm is favourable)
Cutting depth: max. 0.2 mm(very good results are achieved at 0.1 mm)
Cutter material: CBN (Cubic Boron Nitride)Due to the variety of offered cutting materials, we recommend contacting thecutting material manufacturer.
Hardness: 55 65 HCR
Recommended roughnessparameters:
Ra0.1 0.8 m
Rz1 4 mR
max< 8 m
Achievable qualities: Roundness < 2 mTrue running < 2 mTolerances from IT 5 IT 6Roughness R
zvon 2 4 m
Roughness Ravon 0.2 0.8 m
Surface treatment processes
materials must be utilised depending on
the shaft material. Furthermore, the above
mentioned manufacturing parameterscannot always be copied.
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influenced by the sealing lip design
(profile, lead type), the radial force andabove all, the material. Furthermore, the
pumping effect is dependent on the
operating conditions themselves, i.e.
primarily from the circumferential speed,
the lubricant temperature and thus the
lubricant viscosity.
Suitability of Simmerrings even for criticaldirection of rotationNumerous tests at Simrit have shown that
Simmerrings on turned shaft surfaces
reliably seal even with "critical" direction
of rotation of the shaft. Not only the turning
parameters such as
cutting speed
feed rate
cutting radiuscutting material
were varied for the test, but also the
operating conditions:
Circumferential speed
Lubricant temperature
Lubricant type
Pressure
Axial movement
Direction of rotation
Shaft diameter
Furthermore, various sealing variants were
considered in the tests:
Profi lesPumping features (uni or bi directional)
Materials (NBR, FKM, ACM, PTFE)
The knowledge and experiences reveal that:
Simmerrings are perfectly capable of
reliably sealing hard or soft turned
surfaces (see also manufacturing
parameters attachment).Depending on the direction of rotation
of the shaft, the surface structure can
additionally support the sealing effect
of the Simmerring.
If the Simmerring is correspondingly
constructed, it can also seal reliably
in both directions.
The friction torque behaviour of
Simmerrings on turned shafts isqualitatively and quantitatively
comparable with that of ground shafts.
Surface treatment processes
Fig. 51:REM image of a milled shaft
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Producing high quality surfacesA high quality surface is still a prerequisitefor a shaft seal to work reliably.
The surface quality of turned shafts is
significantly infl uenced by the
machine rigidity
tool cutting geometry/cutting material
stability of machine tool
Before the design engineer thus determines
the "turning" process and the manufacturing
parameters, he/she should consult with the
seal manufacturer [enquiry form at
www.simrit.com].
Tangential turningTangential turning is a new, innovative
and highly efficient alternative to themanufacturing processes up to now for
running surfaces of radial shaft seals. The
Fig. 52: REM image of an improperly machined, turned shaft surfacewith typical "chatter marks" which are caused by vibrations
process is based on the kinematics of the
turning space with a linear feed rate andfeatures:
Shorter main times as with conventional
turning
High tool service life
Possible integration in CNC machines
Avoidance of disadvantages of plunge-cut
turning (chatter marks etc.)
Almost completely burr free
Processing of hard and soft surfaces
The maximum processing width amounts to
28 mm even for hard shafts.
Typical, consistently achievable surface
qualities lie between Ra0.2 - 0.6 m and
Rz1 - 3 m.
Fundamental tests at Simrit have confirmed
that tangentially turned, hardened shaftsurfaces are suitable in principle for
Simmerrings.
Fig. 53: Tangential turning of shafts
Surface treatment process
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Fig. 54:REM image of a tangentially turned shaft
Roller burnishingRoller burnishing promotes a strengthening of
the shaft surface. Since this finishing processis often used on shafts, e.g. to increase notch
impact strength for vibrating loads, especially
step-diameter-changes, it is convenient to work
the seal counter surface at the same time.
In addition to straightforward surface
strengthening, this process has the
advantage of neutralising the lead in the
turned basic structure [see Fig. 56].
Due to the high specifi c pressure on thesurface, the "peaks" are pressed down into
the valleys. In the normal case, this will have
the primary effect of, at times drastically
reducing the surface roughness value and
accordingly increasing the load bearing
proportion of the profi le. On a surface which
is too smooth, though, we know that a liquid
will give relatively poor wetting. Thus, under
certain loads, it is difficult for a lubricant filmto form or to be sustained. Depending on the
operating conditions, this can result in thermal
overload at the sealing edge of the shaft seal.
Tests at Freudenberg have indicated that rollerburnished finishes are suitable as counter
surfaces for Simmerrings.
Adherence to the manufacturing parametersis importantA prerequisite is that the surface
roughness values should be as follows:
Ra0.1 - 0.8 m
Rz0.8 - 5 m
Rmax
< 7 m
Prior to roller burnishing it is important that
the shaft surface is turned under defi ned
conditions e. g.:
Pre-machining of shaft at:
feed: 0.05 mm
cut speed: 300 m/min
cut radius: 0.8 m.The subsequent roller burnishing process must
also be performed under precisely controlled
parameters. If it is possible to ensure that the
whole process is reproducible and that the pre-
set parameters can be adhered to, then the
following points can be stated:
Fig. 55:Finish rolling of shafts
Surface treatment processes
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Simmerrings work perfectly on roller
burnished surfaces.The function is independent of the direction
of rotation.
The magnitude of the frictional torque or
power loss is not greater than on ground
surfaces.
The wear caused by the seal into the shaft
is reduced because of the strengthened
surface.
Permissable limits with regard to operatingconditions have not yet been completely
determined. Experience indicates that
peripheral speeds of 20 m/s at oil sump
temperatures up to 130 C subject to the
correct selection of seal, will cause no
problems.
Before the manufacturer finalises the roller
burnishing process and the production
parameters, he/she should consult with theseal manufacturer [you can find an enquiry
form for this purpose at www.simrit.com].
Peening
Peening of shafts is also used forstrengthening components (e. g. turbine
blades). In this process the shaft surface is
"blasted" with steel, glass or ceramic beads.
This causes surface strengthening depending
on the blast energy [see Fig. 57].
An addittional effect of this process is that
lubricants adhere excellently to the crater-like
surface structure, and, in particular, wet them
effectively [see Fig. 58].
Fig. 56:REM image of a finished rolled shaft
Fig. 57: Blasting of shafts
Surface treatment processes
Fig. 58: REM image of a blasted shaft
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For shaft seals this is an advantage, because
it enables a permanent exchange of lubricantunder the sealing contact.
Frictional torque and hence the power loss of
radial shaft seals on peened surfaces is
therefore 1030 % less than on ground
shafts, depending on operating conditions.
The sealing edge temperature is therefore
correspondingly lower. The results of this is
that the service life of seals, especially at
high load (peripheral speed, oil sump
temperature), is substantially increased.
Damaging oil carbonisation is also
significantly reduced.
This effect also produces a marked reduction
in harmful oil carbonisation. And although
no increase in hardness can be measured
by means of the normal hardness measure-
ment methods, the localised wear on theshaft in the area of the sealing lip is also
markedly less.
Peened structures are also suitableas counter surfacesProcess parameters have to be defined and
adhered to in order to produce the most
favourable surface texture:
peening shot (nature and diameter of
beads): corundum or steel chips are not
suitable materials, because an undefined
structure will be produced as the result
peening pressure
peening duration
peening direction
After the peening process, the surface has
to be cleaned of peening shot dust.If axial movement of the shaft is likely to
occur, it is advisable to polish the peened
surface in order to achieve a slight rounding
of the "crater" peaks. This will reduce wear
on the sealing edge of the radial shaft seal.
In the same way as was found on turned
surfaces, the pump action of the seal must
be large enough to compensate for the
lubrication state, which may actually be too
effective, or to transfer back any micro
leakage into the unit being sealed.
Neutral basic structure necessaryThe peening process is simple and, above
all, cost-effective and can be used to cover-
up minor surface defects (up to approx.
50 m).Here too, the designer should hold
consultations with the seal manufacturer
when he stipulates "peening" and the
process parameters.
Honing, SuperfinishingA criss cross surface texture is created
through honing or superfinishing. This has the
advantage that the lubricant binds well to itand that a sufficient lubrication is ensured
even under adverse conditions. This positive
structure for the lubricating film adherence is
achieved by the tool performing translatory
movement while the shaft rotates. A criss
cross structure results which appears neutral
at first glance.
Surface treatment processes
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Honed or superfinished surfaces are only conditionally
suitable as running surfacesThe lubrication ratios are excellent and the
wear of the mating components is small,
however, such structures are not suitable as
counter direction points for radial shaft
seals. While the occurring leakages are in
most cases relatively small, they are not
acceptable in most cases. For pure grease
sealing, the problems are, however,
negligible.
Polishing of surfacesIn the past it was quite common for the
running surfaces of radial shaft seals to be
polished. In the case of repair inparticular,
polishing is still a widely used method for
eliminating small damages or removing dirt.
Often expensive components that werefaultily ground can still be remachined by
polishing [see Fig. 60].
Fig. 59: Honing process
Fig. 60: Polishing of surfaces
While the polishing of surfaces is a cost-
effective process, the disadvantage of thistype of machining is, however, the same as
with grinding: A leading structure on the
surface can be created by the polishing.
If polishing is used as a machining method,
the same roughness parameters as for
grinding are to be adhered to.
Other processes
Outer grindingOuter grinding of shafts creates a
similar structure as with the honing
process. The criss cross structures can
not be reliably sealed.
Plunge-cut turningPlunge-cut turning creates a neutral,
i.e. lead-free, surface texture on the
shaft surface. This is principally suitableas a counter direction point for
Simmerrings.
Surface treatment processes
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Quickpoint grinding
Empirical data for quickpoint grinding isinconclusive. At the moment, no well-
founded statements on the general suitability
can be given. Quickpoint ground shafts can
only be used for one direction of rotation
due to their distinctive leading structure
("conveyance" into the sealed space).
Deep-drawn platesDeep drawn places are frequently used for
repair work. Since a remachining of the
shaft is often not possible, the surface is
cleaned and resanded where necessary.
Subsequently, a deep-drawn plate is drawn
on. This then represents the running surface
for the Simmerring.Fig. 62:Deep drawn plate as counter directionpoint of the Simmerring
Deep-drawn plates can be sealedSealing can be just as reliable on such
surfaces (depending on the operating
conditions) as on ground surfaces.
A prerequisite is no damage of any kind:
No pores or blow holes
No scratches or scoring
No material inhomogenities
In order to ensure this, only materials of
the correct quality should be used.
Although the materials used are relatively
soft, they possess suffi cient abrasivewear-resistance due to the reforming
process.
Surface treatment processes
Fig. 61:Plunge-cut turning of shafts. While successful applications were realisedfor soft machining, machining with hardened material is more difficultdue to the tendency to chatter
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Fig. 63:Determination of lead on the shaft with the thread method
Movement of the thread =Oil conveyance direction
PencilMark
Movement of the thread =Oil conveyance direction
Shaft with right turningthreads
=Radial shaft seal with left-
leading
Shaft with left turning threads=
Radial shaft seal with right-leading
Leading test
Leading test
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Fig. 64: Example of a "calculated" surface structure
Leading measurements
Besides the adherence to the specifiedroughness variables like R
a, R
zand R
max, the
surfaces from plunge-cut ground shafts, as
mentioned already, should be lead-free.
The complete test whether the lead-free
requirement is fulfilled is difficult to conduct.
There are no measuring methods with which
a lead orientation can be reliably measured.
Despite this, representative results can be
determined using the widely used thread
method. A special thread is wetted with oil
and is placed over the shaft to be tested. A
weight (approx. 50 g) ensures an even
enlacement of the shaft. If the shaft rotates,
the thread begins to move axially if a lead
is present.
Although it is not possible to quantitativelyrecord the slope of the lead, this method has
proven itself in practice. It is applied in
slightly varying forms around the world. In
many cases, surface structures that are
damaging to a radial shaft seal can be
proven using this simple method. However,the method has weaknesses. With very small
or very large lead structures, the thread
does not react demonstrably.
All attempts to develop an alternative
method of measurement have failed in the
past. The approach of determining the lead
structure using a mathematical description of
the surface according to the measurement of
the surface texture appears promising [see
Fig. 64].
Still, the measurement and evaluation times
are so high that an implementation in the
production is not always cost-effective. But if
the required hardware and software is
developed in the foreseeable future, this
measuring method could help solve many
problems or help to understand the infl uenceof the various process parameters on the
surface quality.
Leading test
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Summary
The surface texture of the shaft infl uences the sealing function
of a Simmerring signifi cantly.
The manufacturer must therefore ensure that the specifi ed
manufacturing process and roughness parameters are
adhered to and that the process is stable.
Besides these requirements, the selection of the correct
machining method determines the ideal system design in
terms of cost-effi ciency and technology. Alternatives to the
proven but expensive plunge-cut grinding exist and were
studied. Reliable sealing is achieved when the Simmerring
is capable of returning the microleakages created by the
shaft surface back into the sealed space.The design engineer has to determine the most functional and
cost-effective combination for the radial shaft seal/machining
method during the planning phase. But before the design
engineer makes a final selection, he/she should define the
process parameters together with the seal manufacturer and,
considering the actual operating conditions, determine the
ideal radial shaft seal. For protection or final verification,
aggregate tests should be performed.
Use our fax form at www.simrit.de, so that we can developthe optimum solution together with you.
Summary
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