me 551 - 05 structural design (rev. 1.2)
TRANSCRIPT
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Outline – Machine Structures• Design Requirements
• Structural Elements
– Materials
• Design Considerations –
– Beds
• Manufacturing Techniques
– Cast Iron
– Welded Steel
– Polymer Concrete Casting
– Granite-based Structures
– Carbon Fiber Composites
• Structural Damping• Finite Element Analysis
• Elimination of Static Deformations
Chapter 5 ME 551 2
Desi n Re uirements
• Structure of the machine houses (and supports the
operation of) all the vital (moving or stationary) elements of
the machine.
– s e s e e on o e mac ne. – Without a good structure, the rest of the machine will be ineffective.
– Symmetrical (and Simple) Design
– Minimum Wei ht
– High Static and Dynamic Stiffness
– High Structural Damping
– High Secular and Thermal Stability
– Independent Foundation
Chapter 5 ME 551 3
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Structural Elements• Structural elements can be
Flat Bed
– Machine Beds
• T-Bed, Slanted Bed,
• Floor Plates, etc.
– Columns
Slanted Bed
– Portals/Bridges
• Open or Enclosed Design
• Machine structures can be
categorized into three classes: – Open Frame
– Closed Frame
– -
Chapter 5 ME 551 4
O en Frame Structures1,2
• Most traditional machine
tools employ this
configuration.
– Also known as C- or G frames
• Provides eas access to the
workspace.
•
frames.
.
• Prone to Abbe offset errors.
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Closed Frame Structures1,2
• Most precision machine
architecture:
Deformed Frame
–
frames Axial Force
Tool
is fairly easy.Structural Loop
(“Force Flow”)
• ymme r ca s ruc ure s
quite rigid.
Workpiece
• Main actuator must be
located on the bridge.
Chapter 5 ME 551 6
Truss-t e Structures
,
are deployed:
– Cubic / Cuboid
– Tetrahedron
– Octahedron etc.
• Such (truss-type) geometries yield stable- and strong
enclosed structures that are especially suitable for parallel
mec an sms e exapo p a orms .
– High thermal stability
dimensions of the frame.
Chapter 5 ME 551 7
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Exam le - Octahedral Hexa od
• Machine is built by Ingersoll Company
• It employs an octahedral geometry to
support the hexapod “tool” platform.• The hexapod (Stewart platform
concept originally developed for flight
freedom.
–
degrees from the vertical.
• Advanced controller architecture andalgorithms make programming
possible.
Chapter 5 ME 551 8
Structural Materials
Ferrous metals Nonferrous metals Non-metals
Com osites
Cast IronSteel
Al. (Cast 201) Al. (6061-T651)
GraniteZerodur ™
Invar
Super Nilvar ™
Copper
Brass (Cu Alloy)
Polymer concrete
Portland concrete
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Column Structures1
With Ribs
Chapter 5 ME 551 10
Stiffness Pro erties of Columns1
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Bed Structures1
Chapter 5 ME 551 12
Bed Structures Cont’d
Chapter 5 ME 551 13
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Pro erties of Bed Desi ns1
Chapter 5 ME 551 14
Cast Iron Structures2
• Widely used in machine
• Stable with thermal anneal,
,
relieve
•
heat transfer
• Low cost for moderate sizes
• Integral features can be cast
in place
• Design and manufacturingrules are well-established.
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Welded Steel Structures2
• Often used for larger
-
• Stable with thermal anneal• ow amp ng, mprove w
shear dampers
• Integral features/parts can be
• Structures can be made from
tubes rofiles and lates.
Chapter 5 ME 551 16
Pol mer Concrete Castin 2
• Polymer concrete (PC) is a relatively new
design.
– Special polymers are mixed with specially
prepared/sized aggregate. – Epoxy-granite-, mineral-, and reactive-
same technique.
• For PC castings, the same rules for draft
allowance apply as for metal castings if
the mold is to be removed.
– ,
develop hot spots while curing even inthick, uneven sections.
Chapter 5 ME 551 17
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PCC Cont’d
• ,
internal foam cores to maximize their
stiffness-to-weight ratio.
• PC can accommodate cast in place
components such as bolt inserts,
conduit, bearing rails, hydraulic lines
etc.
• g y oa e mac ne su s ruc ures
(e.g. carriages) are made from cast
.
Chapter 5 ME 551 18
PCC Cont’d
• PC structures can have the stiffness
of cast iron structures.
– They can have much greater damping.
• PC does not diffuse heat as well ascast iron.
– Attention must be paid to the isolation of
heat sources to prevent the formation of
hot spots.
• When bolting or grouting non-PC
components to a PC bed, bimaterial
effect must be considered.
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Granite-Structures• Used exclusively in precision instruments and
CMMs.
– Serves as reference planes/surfaces
– Quite costly• ,
– It must be sealed off properly to avoid
absorbtion of water. Otherwise, it will distort!
• This very hard (and brittle) material is very
stable:
– 3.
– Elasticity modulus: 40 [GPa]
– Tensile strength: 16 [MPa]
– erma exp. coe c en : . × -
• Not all grades are suitable for precision
machine design.
Chapter 5 ME 551 20
Carbon Fiber Com osites3
• Fibre reinforced composites have
very g va ues o a spec c
modulus of elasticity and specific
strengt . – Mechanical properties can be tightly
contro e
– Joining process can be complicated
– Quite expensive
• The application of this new material
to this field is still in its early stages.
Chapter 5 ME 551 21
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Slanted Bed Desi ns for Lathe1
Cast iron guideway plate
on cast concrete
Adhesive Joint
Adhesive Surface
Location of Cast-ribs
Lower Section
Steel Insert for
Mounting for
Hydraulics
of Bed
Machine Foot
Transfer TaConduit
Oil Chamber
Chapter 5 ME 551 22
Turning Fixture
Structural Dam in
• Damping is needed to absorb energy from the process:
– o preven c a er an amage o e sur ace
– To absorb energy from structural modes excited by the servos
and other sources
• Damping can be obtained by internal means:
– Material damping
– Damping by micro-slip at joints
• Damping can be obtained by external means:
– Constrained layer dampers (or shear dampers)
– Vibration absorbers
–
• Velocity control loops in servo systems• Actively controlled masses attached to the structure
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Combined Dam in Effect6
• Major part of the damping for a machine system can be generated at
the mating surfaces (i.e. bolted joints, slides) of the various
- .
Chapter 5 ME 551 24
Shear Dam ers4
• Steel structures are known to
ave e n erna amp ng.
• One alternative method to
structure is to employ shear
dam ers.
• Visco-elastic layer damps
motion between structure and
constraining layer (from
bending or torsion) by
ss pa ng ne c energy n o
heat.
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A lication - Shear Dam ers4
,
considered.
– Inner tube serves as constrainin la er.
– Constraining layer is wrapped with damping material.
– Coated inner tube is inserted and gap filled with epoxy.
Chapter 5 ME 551 26
A lication Cont’d
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Exam le - Precision Grinder 7
T-bed of the precision grinder includes
-
inserts. Square inserts also allow the
circulation of cooling fluid.
ross-sec on o e s ear
damped test beam
Chapter 7 ME 551 28
Vibration Dam in Ta es• Vibration damp(en)ing tape/foil is a
“ - ”
damping.
• Commercial roducts like 3M
434/435/436™ constitute a visco-elasticpolymer coated on a soft Aluminum
constraining layer.
• Very useful in dampening the vibrations
o me a p a es an compos e pane s.
• Somewhat sensitive to high
– Nominal operating temperature range (forthe tape) is -60 to 20oC.
Chapter 5 ME 551 29
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Vibration Absorbers1
a g n
i f i c a t i o n
f u n c t i o n
M
Chapter 5 ME 551 30
Absorber Desi ns2
TMD
Constrained-
Layer Beam Adjustable Position
Anchor Mass
Chapter 5 ME 551 31
ruc ure
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Finite Element Method• FEM is an indispensible engineering analysis tool
to find a roximate solutions to technical
problems defined by partial differential equations.
• FEA Packages (ANSYS™, MARC/Mentat™,
Nastran/Patran™, Abaqus™, etc.) are routinely
utilized to design/analyze/optimize structural
.
• Large number of engineering analysis can be
conducted b FEA acka es:
– Stress/Strain (in elastic- or plastic region)
– Heat Transfer – Mechanical Vibrations
– Electromagnetic Fields (Maxwell™)
–
Chapter 5 ME 551 32
FEM Anal sis1CAD Model of the Machine “Specs” of the Simulat ion
Determination of the
simulation ob ectives
■
Abst raction for the
FE-model Creation Abstrac tion of Guides
and Drives as Springs
(deformations, stresses,
natural modes)
Determination of modeling
strategy (volume- or shell
■
Choice of element order(linear, parabolic)
■
Presentation of the Results
Definition of boundary conditions
(force, temperature) and constraints
■
List of basic stiffness
Program’s Internal Processes
■
Compilation of the Overall Model
matrices
Structure the global
stiffness matrix
Consideration of the
boundar conditions
■
■
Solution of the resulting
linear systemDerivation of stress from
deformation values
■
■
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FEM Anal sis - Illustration1
Chapter 5 ME 551 34
Example – Portal Frame1
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Vibration Anal sis - Illustration1
Chapter 5 ME 551 36
Natural Fre uencies & Modes1
Natural Frequency: 42.4 Hz Natural Frequency: 73.4 Hz Natural Frequency: 102 Hz
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Vibration Anal sis1 Cont’d
Chapter 5 ME 551 38
Frequency [Hz]
Elimination of Static Deformations5
• ere are ree me o s
to compensate the elastic
machine structure under
-
loads:
a. ompensa ng curve
b. Preloaded support
c. Counter-weight
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Com ensatin Curve1
• The bearing rails are finished (grounded) so that
they deform to the desired shape when themachine axes move.
– Grinding process is expensive but it saves structural
costs.
• When the primary weight is that of the machine
axis (not the workpiece!), this method can be
very effective.
Chapter 5 ME 551 40
Counter-wei ht S stems
• For vertical axis, the servo-motor
system needs to support the dead-
weight of that axis.
– ay nee o c oose overra e servo-system.
– Ener wasted due to IR losses of
machine.
• Dead weight can be supported by an
external system (i.e. counter weights,
hydraulic systems, floats, etc).
• or ynam c mo ons, mo or a -
screw inertia usually dominates.
Chapter 5 ME 551 41
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Counter-wei ht Cont’d• Counterweight system contributes to the
– Cogging effect, elastic effect etc.
, ,
utilized to carry the counterweight.' – ,
as it rotates producing a small cogging effect.
•
least variation in force.
– Cables are elastic com ared to chains and hence the shouldonly be used for quasi-statically (i.e slow) moving elements.
– Pulley friction and friction in the counterweight's bearings should
.
Chapter 5 ME 551 42
Some Desi n Rules2
• ,
golden rectangle (Height/Width = 1.618) in mind.
• Utilize s mmetr wherever ossible.
• Minimize the structural loop and use closed sections
whenever possible.
• Large plate sections should be stiffened with ribs and
other means to kee them vibratin like drumheads. – When needed, use active damping systems.
• Maximize thermal diffusivit of the machine and
minimize heat input.
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Desi n Rules Cont’d• Locate the work volume at the center of mass and in plane
.
• Start at the tool tip (or workpiece) with estimates on
cuttin forces and acceleration
– Then work backward through the structural system.
– Use guesstimates for sensor, bearing, and actuator limitations to
help size structural components.
• Try to make the natural frequencies of the various
. .
together.
– .
• Use as many design tools as possible in design stage.
– Especially, Solid Geometric Modeling and FEM Packages.
Chapter 5 ME 551 44
References
1. M. Weck, C. Brecher, Werkzeugmaschinen (Band 2), Springer-
, .
2. A. H. Slocum, Precision Machine Design, SME Press, 1992.
• A. H. Slocum, ME 2.075 Course Notes, MIT, 2001.
3. L.N. L. deLacalle, A. Lamikiz, Machine Tools for High PerformanceMachining, Springer-Verlag, 2009.
. . , , , .
5. Cranfield Unit for Precision Engineering (CUPE), Precision
Engineering Course Notes, Cranfield Institute of Technology (UK),
1998.
6. Löwenfeld, K., “Zweites Forschungs und Konstruktionskolloquium
Werkzeu maschinen ” . 117 Vo el-Verla Cobur 1955.
7. E. R. Marsh, A. H. Slocum, “An integrated Approach to StructuralDamping,” Precision Engineering, vol. 18, pp. 103-109, 1996.