design and modeling of fluid power systems - purdue … · dr. monika ivantysynova maha professor...
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Dr. Monika Ivantysynova
MAHA Professor Fluid Power Systems
Design and Modeling of Fluid Power SystemsME 597/ABE 591 Lecture 5
MAHA Fluid Power Research Center
Purdue University
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5912
Axial piston pump design solutions (swash plate and bent axis)
Radial piston pumps and motors – piston support
Gear Pumps – internal and external – axial and radial gap compensation
Vane pumps – advantage and disadvantage of this design
Displacement Machines
Study different design principles and learn about the following topics
Aim: - To be able to select the right design for your system application!
- Knowledge about limitations of each basic design
- To apply models on system level for each design
Please study the appropriate chapters in
Ivantysyn, J. and Ivantysynova, M. (2001), Hydrostatic Pumps and Motors.
Akademia Books International. New Dehli. ISBN-81-85522-16-2
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5914
Bent axis axial piston pumps
18
Synchronization of cylinder block
Using a universal joint
Using a bevel gear
Cylinder block
Driving flange
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5915
Bent axis axial piston pumps
19
Cardan joint
Synchronization of cylinder block connecting rod
Synchronization by pistons
piston
Piston rod
Synchronization by piston rod
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5916
Kinematics of bent axis pumps
20
Frame (1)
Driving flange (2)
Piston (3)
Cylinder (4)
Four link 3D mechanism
Assuming a fixed connection between link 2 and link 4, achieved by
synchronization
mechanism has finally two degrees
of freedom
Five link 3D mechanism
Frame (1)Cylinder (4)
Piston (3)
Driving flange (2)
Piston rod (5)
the mechanism has finally three
degrees of freedom
Piston can rotate about z 3 -axis
Piston can rotate about z3-axis and
piston rod can rotate about z5-axis
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5917
Piston Design
16
Short piston with piston rod
Spherical piston with piston ring
Long piston with piston rod
Conical piston with piston rings
Synchronization by
universal joint or bevel gearSynchronization by
pistons or piston rods
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5918
Design Examples
22
Driving flange bearings
Spherical valve plate
Pump control device
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5919
Design Examples
23
Conical piston
Spherical valve plate
Driving flange bearingsFixed displacement pump
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59110
Radial Piston Pumps
with external piston support with internal piston support
eccentricity
Suction
Delivery
Stroke ring
Rotating cylinder body
29
Stationary cylinder body
Rotating cam or crankshaft
Suction
Delivery
Displacement volume adjustable by changing eccentricity e
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59111
Radial Piston Pumps
30
with external piston support
Multiple stroke radial piston pumps
Stationary stroke ring
Rotating cylinder body
with internal piston support
Stationary cylinder body
Rotating cam
Only fixed displacement pumps realizable!
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59112
Piston support on outer stroke ring
16
Stroke ring
Stroke ringPlane valve plate
Rotating cylinder body
Piston
Piston rotation enforced
by friction force Ff
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59113
Piston support on outer stroke ring
17
Stroke ring borne in roller bearings
Stroke ring
Piston roller guide
Piston
Piston sliding bearing
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59114
Piston support on outer stroke ring
18
Ball joint inside the piston
Slipper support Stroke ring
Hydrostatically
balanced slipper
Hydrodynamically
balanced slipperSlipper pocket
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59115
Stroke ring support
19
Using a sliding carriage supported using line contact
Stroke ring mounted on a pivot
Change of eccentricity by pivoting
the stroke ring about pivot axis
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59116
Design Example
20
Control journal
Slipper
Stroke ring
Piston
Pump control system
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59117
External gear pump
13
Basic principle
Inlet Outlet
Driving gear
Driven gear
Housing
Axial gaps between housing and the gear pair must be very small to seal the
displacement chamber
Radial gaps between teeth addendum circle and housing
Se QnVQ
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59118
Two stage gear pump
14
Driving gear
Driven gearDriven gear
Inlet 1
Inlet 2
Outlet 2
Outlet 1
Outlet 1 and inlet 2 can be connected
or the pump can have two separate outlets
p1
p2
p4
p3
121 ppp
342 ppp
p2 = p3
p1 = p3
21 pp the driving gear is pressure balanced!
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59119
Internal gear pump
15
PinionInternal gear (ring gear)
Suction zonePressure zone
Crescent shaped divider
Using teeth of standard involute design requires a combination where the
pinion has two or more fewer teeth than the ring gear! Pinion and ring gear
are then separated by a crescent shaped divider.
Advantages:
Better suction ability
Higher efficiency
More compact design
Less noise emission
Longer duration of teeth meshing leads to better sealing function
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59120
Internal gear pump
16
Many different tooth profiles have been applied in the recent past.
Crescent shaped divider
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59121
Annular gear pumps
Applying specially generated tooth curves it can be achieved, that the inner
rotor (the pinion) has only one tooth less than the ring gear, thus eliminating the
crescent-shaped divider.
Gerotor pump
Each tooth of the pinion maintains
continuous sliding contact with a
tooth of the ring gear, providing
fluid tight engagement.
Relative sliding velocity between
pinion and ring gear is very small
quiet operation and long
service life
Outlet Inlet
17
112 zz
Ring gear (z2)
Pinion (z1)
1
1
1
2
1
2
1
12
11
11
zn
zn
z
znn
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59122
Annular gear pump – Orbit principle
Ring gear (z2) fixed112 zz
Displacement volume is
given by z1 times z2 tooth
spaces
Multiple delivery of
each tooth spaceRotating
distributor
InletOutlet
Rotating pinion (z1)
2 Pressure port
1 Suction port
18
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5912318
Pressure compensated axial gaps
Sealing ring
Sliding bearing
Gear pair
Bearing bushings
Shaft seal
End cap Front coverhousing
Pressurized area A
Only one direction of shaft rotation possible!
2
3.11.1p
FA z
FZ FZ
Axial gap
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59124
Pressure compensated axial gaps
19
Pressurized area
Driving gear
Driven gearSliding bearings
Sealing
Axial gap – pressure compensated
Improved volumetric efficiency
2
23.11.1
p
FA z
2FZ
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5912520
Pressure compensated radial gaps
Radial gap compensation
Pressurized area
Axial gap compensation
Bearing bushing
Small pressure zone achievable
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59126
Gear pump – design example
20
Shaft seal
Bearing bushing performing a radial and axial gap compensation
Driving gear
Driven gear
inletoutlet
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5912721
Internal gear pump- design example
Ring gear Pinion
special shaped divider
Internal gear pump with axial and radial gap compensation
inlet
outletMoveable bearing shellPressurized area
Radial gap compensation
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5912822
Screw Pumps
With two meshing screws
inlet
outlet
With two meshing screws
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5912923
Screw Pumps
With three meshing screws
outlet
t…thread pitch
inletoutlet
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5913036
Vane Pumps
Classification of vane pumps
Unbalanced vane pump
RotorStator
Balanced vane pump
Only fixed displacement pumpFixed and variable pump design
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 59131
Vane pumps- basic working principle
37
inlet
inlet
outlet
Single stroke vane pump – variable
displacement volume
Large radial forces exerted on the rotor
Limitation of max. operating pressure (20 MPa)
Overcentre pump – the direction of flow can be re-
versed by change of eccentricity, i.e. without
changing the direction of rotation of the drive shaft outlet
no flow!Relatively high friction between
axial moveable vanes and rotor
&
between vanes and stator
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5913238
Vane pumps- classification
Multiple stroke vane pump
Rotor
Rigid vane pump
SICFP’05, June 1-3, 2005, Linköping
© Dr. Monika IvantysynovaDesign and Modeling of Fluid Power
Systems, ME 597/ABE 5913339
Fluid distribution
Internal fluid distributionExternal fluid distribution
inlet
outlet
Distributor - fixed control journal
rotor
stator