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![Page 1: Design and Modeling of Fluid Power Systems · PDF fileDesign and Modeling of Fluid Power Systems ME 597/ABE 591 Lecture 4 ... due to compressibility of a real fluid K A.. adiabatic](https://reader034.vdocuments.us/reader034/viewer/2022051304/5a78b8607f8b9ae91b8e7dbb/html5/thumbnails/1.jpg)
Dr. Monika IvantysynovaMAHA Professor Fluid Power Systems
Design and Modeling of Fluid Power SystemsME 597/ABE 591 Lecture 4
MAHA Fluid Power Research CenterPurdue University
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5912
Displacement machines – design principles & scaling laws
Power density comparison between hydrostatic and electric machines
Volumetric losses, effective flow, flow ripple, flow pulsation
Steady state characteristics of an ideal and real displacement machine
Torque losses, torque efficiency
Content
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5913
Historical BackgroundHydrostatic transmissiom
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Gear pump Axial Piston Pump
Vane pump
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5914
Displacement machine
2
Pumping
Suction
Vmin=VT with VT .. dead volume
Adiabatic compression
Adiabatic expansion
due to compressibility of a real fluid
KA.. adiabatic bulk modulus
Te , n
p1
p2, Qe
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5915
Displacement machine
due to viscosity & compressibility of a real fluid
3
Pump Motor
Port pressure Port pressure
Pressure in displacementchamber
Pressure in displacementchamber
Pressure drop between displacement chamber and port
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5916
Power Density
Electric Motor
with I current [A]B … magnetic flux density [ T ] or [Vs/m2]
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Torque:
J… current density [A/m2]
r
r
b
I = J b h
Hydraulic Motor
Fh = p ⋅ L ⋅h
T = p ⋅L ⋅h ⋅ rT = I ⋅B ⋅L ⋅ r ⋅ sinα
Fe = I ⋅B ⋅L ⋅ sinα
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5917
Example
Power:
For electric motor follows: assuming α=90°
For hydraulic motor follows:
Force density: Electric Motor Hydraulic Motor
with a cross section area of conductor:
34
P = T ω = T 2π nP = I B L r 2π n
9 10-6 m2
up to 5 107 Pa
P = p ⋅L ⋅h ⋅ r ⋅2π ⋅n
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5918
Mass / Power Ratio
Electric Machine Positive displacement machine
mass
power= 1 …. 15 kg/kW 0.1 … 1 kg/kW
10 times lighter
min. 10 times smaller
much smaller mass moment of inertia (approx. 70 times)
Positive displacement machines (pumps & motors) are:
much better dynamic behavior of displacement machines
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5919
Displacement Machines
Fixed displacement machines Variable displacement machines
Piston Machines
Gear Machines
Screw Machines others
Axial Piston Machines
Radial Piston Machines
In-line Piston Machineswith external piston support
Swash Plate Machines
Bent Axis machines
Annual Gear
F
F
F
6
with internal piston support
External Gear
Internal Gear
Vane Machines
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59110
Axial Piston Pumps
Te , n
p1
p2, Qe
Inlet
Outlet
Swash plate Piston Valve plate(distributor)
Cylinder block
Cylinder block Pitch radius R
Piston stroke = f (ß,R)Variable displacement pumpRequires continous change of ß
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59111
Bent Axis & Swash Plate Machines
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Torque generation on cylinder block
FR
FR
FR
Fp
Fp
Fp
FN
FN
FN
Torque generation on „swash plate“
Swash plate design
Bent axis machines
Radial force FR exerted on piston!
Driving flange mustcover radial force
Fp FN
FN
FN
Fp
FR
FR
FR
Fp
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59112
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Axial Piston Pumps
Openings in cylinder bottomIn case of plane valve plate
In case of spherical valve plate
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59113
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Axial Piston Pumps
OutletInlet
Inlet opening Outlet opening
Plane valve plate
Plane valve plate
Connection of displacement chambers with suction and pressure port
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59114
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Axial Piston Pumps
InletOutlet
Kinematic reversal: pump with rotating swash plate Check valves fulfill distributor function
Suction valve
Pressurevalve foreach cylinder
can only work as pump
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 5911522
Comparison of axial pistonpumps
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59116
ideal displacement machineSteady state characteristics
8
Displacement volume of a variable displacement machine:
0P
0
P
n
0
T
0Q
0
Q
n
0
T
n
V = α Vmax
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λ
λ
λ
λ
λ
λ
© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59117
Te , n
p1
p2, Qe
Scaling laws
The pump size is determined by the displacement volume V [cm3/rev]. Usually a proportional scaling law, conserving geometric similarity, is applied, resulting in stresses remaining constant for all sizes of units.
Assuming same maximal operating pressures for all unit sizes and a constant maximal sliding velocity !
… linear scaling factor
9
Q = V n
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59118
Example
The maximal shaft speed of a given pump is 5000 rpm. The displacement volume of this pump is V= 40cm3/rev. The maximal working pressure is given with 40 MPa. Using first order scaling laws, determine:- the maximal shaft speed of a pump with 90 cm3/rev- the torque of this larger pump- the maximal volume flow rate of this larger pump- the power of this larger pump
For the linear scaling factor follows:
Maximal shaft speed of the larger pump:
Torque of the larger pump:
Maximal volume flow rate:
Power of the larger pump:
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59119
Te =
Real Displacement Machine
Te , n
p1
p2, Qe
QSi
QSe
Inlet
Outlet
DistributorCylinder
Piston
Effective Flow rate:
Effective torque:
QSe… external volumetric losses
QSi… internal volumetric losses
TS …torque losses
QS … volumetric lossesQe= αVmax n - Qs
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59120
Volumetric Losses
QSL external and internal volumetric losses = flow through laminar resistances:
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Te , n
p1
p2, Qe
QSi
QSe
external internalvolumetric losses
losses due tocompressibility
losses due toIncomplete filling
Dynamic viscosity
Assuming const. gap height
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59121
Volumetric Losses
Effective volume flow rate is reduced due to compressibility of the fluid
Pumping
Suctionsimplified
with n … pump speed
12
QSK = n ΔVB
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59122
Steady state characteristics
of a real displacement machine
Effective volumetric flow rate
13
nmin
Qi = V n = α Vmax n
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59123
Steady state characteristics
Effective mass flow at pump outlet QmeLoss component due tocompressibility does notoccur!
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59124
Instantaneous Pump Flow
Instantaneous volumetric flow Qa
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Volumetric flow displaced by a displacement chamber
k … number of displacement chambers, decreasing their volume, i.e. being in the delivery stroke
The instantaneous volumetric flow is given by the sum of instantaneous flows Qai of each displacement element:
z … number of displacement elementsz is an even number
z is an odd number
Flow pulsation of pumps Pressure pulsation
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59125
Flow pulsation
16
Non-uniformity grade of volumetric flow is defined:
2
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59126
Torque Losses
Torque loss due to viscous friction in gaps (laminar flow)
h…gap height
Torque loss to overcome pressure drop caused in turbulent resistances
l
d v
… flow resistance coefficient
… drag coefficient
constant value
Torque loss linear dependent on pressure
effective torque required at pump shaft
TSρ = CTρ ρ n2
TSp = CTp Δp
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59127
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Steady state characteristics
of a real displacement machine
0T S
µ
0
T Sp
n0
T Sp
T Sρ
0
0 n
T Sρ
0 n
T Sµ
Torque losses
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59128
Steady state characteristics
n0
T
Ti
TSc
TSp
TS
ρTSµ
Effective torque Te
0T
Ti
TSc
TSp
TS
ρTSµ
Effective torque Te
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Effective Torque
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59129
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Piston displacement:
Piston stroke:
HPsP
R … pitch radius
Outer dead point AT
Inner dead point IT
φ=0
KinematicsAxial Piston Machine
z = b tanβb = R - yy = R ⋅ cos ϕ
sp = -R ⋅ tanβ ⋅ (1-cosϕ )
HP = 2 ⋅R ⋅ tanβ
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59130
Kinematic Parameters
24
vPau
vu
aP
Piston velocity in z-direction:
Piston acceleration in z-direction:
Circumferential speed
Centrifugal acceleration:
Coriolis acceleration ac is just zero, as the vector of angular velocity ω and the piston velocity vP run parallel
vu = R ω
au = R ω2
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59131
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Instantaneous Volumetric Flow
Geometric displacement volume:
z … number of pistons
In case of pistons arranged parallel to shaft axis:
Geometric flow rate: Mean value over time
Instantaneous volumetric flow:
with instantaneous volumetric flow of individual piston
k …number of pistons, which are in the delivery stroke
For an ideal pumpwithout losses
Vg = z Ap HP
vP = ω ⋅R ⋅ tanβ ⋅ sinϕ
Qai = vp ⋅Ap = ω ⋅Ap ⋅R ⋅ tanβ ⋅ sinϕ i
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59132
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Instantaneous Volumetric Flow
In case of odd number of pistons:
In case of even number of pistons: k = 0.5 ⋅ z
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59133
Flow & Torque Pulsation
kinematic flow and torque pulsation due to a finite number of piston
Flow Pulsation:
Torque Pulsation
Non-uniformity grade:
Even number of pistons: Odd number of pistons:
tan z tanz zz
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59134
Piston Pumps
kinematic flow and torque pulsation due to a finite number of piston
Flow and torque pulsation frequency f:
f=z·nEven number of pistons:
Odd number of pistons: f=2·z·n
z… number of pistonsNon-uniformity Even number of pistons: Odd number of pistons:
mean mean
NON-UNIFORMITY of FLOW / TORQUE
NON-UNIFORMITY of FLOW / TORQUE
Flow & Torque Pulsation
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59135
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Flow Pulsation
Non-uniformity grade:
Number of pistons z
3 4 5 6 7 8 9 10 11
Non-uniformity grade δ
0.140 0.325 0.049 0.140 0.025 0.078 0.015 0.049 0.010
Volumetric losses Qs=f(φ) and
Flow pulsation of a real displacement machine is much larger than theflow pulsation given by the kinematics
Kinematic non-uniformity grade for piston machines:
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© Dr. Monika Ivantysynova Design and Modeling of Fluid PowerSystems, ME 597/ABE 59136
Flow Pulsation
Flow pulsation leads to pressure pulsation at pump outlet