Advantages Of Hydraulic Tensioning
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Transcript of Advantages Of Hydraulic Tensioning
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Advantages of hydraulic tightening for bolt
connections
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Purpose of a boltConnect at least 2 parts dismountable together
glueing, welding, riveting
Prevent take-off by elongation of the bolt and compression of the parts
Sealing effectsTransmitting shear-forces by friction
Weight-reduction:Use of high-strength bolts with high and exact pretensioning force
Friction µ
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Different modelsScrew-head forms Thread-size + pitch
Standard series, fine series…Thread forms
metric, buttress, trapezoidal, round…
Strength categories: 8.8, 10.9, 12.9
Surface treateningFriction coefficient
FormsNecked down bolts – largeelongations for only little loss of pretensioning!Shoulder studsSpecial bolts
….
default values for pretensioning force
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Bolt loadsAxial operating force
Optimum load: Only axially
Shear-force
Bending moment
TorqueExspecially during mounting
Partly during operation
Often pretensioning to 90% of yield stress for highest load capacities of bolts
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
method advantages disadvantages Tighten-ing factor
Tightening by hand (socket wrench)
cheap, available everywhere
Large deviations in pretensioning forceInapplicable for large thread-sizes
2,5-4
Torque-controlled with torque wrench
Little more expensiveAvailable
Smaller deviations, inknown influence of frictionInapplicable for large thread-sizes
1,7-2,5
Thermical with measuering of elongation (Ultrasonic)
Very precise Only for large clamping length and special screw forms (flat heads)Ultrasonic measuring or exact length measuring for each bolt
1,05-1,2
Tightening methods I
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Tightening methods IImethod advantages disadvantages Tighten-
ing factor
Controlled by yieldstress of torque-angle
precise, Almost independent from friction
Extensive equipment necessary 1,2-1,4
Impact wrench(electric/air driven)
Applicable for large sizes
Large deviation in tightening torque due to designAdjustment is inaccurate, requires measurement of Actual pretensioning forceCounter-torque has to be taken by user or external support
2,5-4
hydraulic High forces achievableDetection of actual force possibleTensioning several bolts at a time
Accessories needed (Pump/Hose…) 1,2-1,6
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Tightening Factor
Tightening Factor kA according to SCHAAF
By Changing the flux of forces during pressurization and releasing pressure a loss of force takes placeDepending on clamping length relation l / dDepending on thread-pitch p
→ kA = 1 / K ≈ 1 - 2
0
0,2
0,4
0,6
0,8
1
0 2 4 6 8 10 12 14 16 18 20
clamping length relation l/d
rem
aini
ng c
lam
ping
rela
tion
K
large pitch small pitch
(Empirical data)
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Calculation base
FV
Precondition for exactdimensioning is the notice of operational loads!!
Tensioning diagram:Calculate pretensioning force from operational loadsCompression and elongationClamping force has to be > 0 during operation
FB
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Depending on tightening method the mounting force can be determined:
FVM= kA x FVmin
kA = tightening factor (1,05-4)FVmin = Min. pretensioning force
Calculation base
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Thread-Friction
Head-Friction
Calculation base
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Torqueing methods lose a lot of torque for overcoming friction inside the thread and below the head:
MA=FVM x (d2/2 x tan (φ+ρ‘) + µk x dk/2)
Calculation base
Thread-friction Head-friction
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
ExampleUsing a torqueing method: transforming torque to axial force by means of inclined plane
Due to friction only little axial forceFriction coefficient has to be estimatedAdditional torque load inside th screw
Result: Little transforming rate from torque to pretensioning force (abt.. 90% loss)For large sizes the torque can not be reached by handLarge deviations when fricitionis unknown
Thread size D[mm]
Pitch P[mm]
Torque MA
[Nm]Friction coeff. µ[-]
Tensioning force FVM
[kN]0 3142
(100%)
0,08 522 (17%)
36 4 2000
0,25 188 (6%)
0 67500 (100%)
0,08 5510(8%)
120 6 64500
0,25 1870(3%)
Abt. 300% difference
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
Preconditions for hydraulic tighteningThread-size and pitch are known
Protruding bolt end is long enough
Design is modified for little losses:
Only few separation planesNo washers necessary. If necessary: place tool directly on washerLarge clamping length
www.schaaf-gmbh.comschaaf_englisch_schraubenverbindung_kat6.ppt · 12.07.2007
ConclusionAdvantages of using hydraulic tightening methods
Friction coefficient has not to be estimatedOnly axial load can be set to the bolt – no torque load due to friction
Bolt size can be reducedForce depends only on the piston area and pressure of the tensioning device – no inaccuracySpecial solutions possible