NUMERICAL AND EXPERIMENTAL ANALYSES OF VANE AND … Frosina.pdfNumerical and experimental analyses...

NUMERICAL AND EXPERIMENTAL ANALYSES OF VANE AND PISTON

PUMPS

University of Naples “Federico II”

Department of Industrial Engineering

Fluid Power Research Group

West Lafayette June 4th, 2019

FPRG – FLUID POWER RESEARCH GROUP

Index

June 4th, 2019Fluid Power Research Group

Numerical and experimental analyses of vane and piston pumps

– FPRG – University of Naples “Federico II”

– Vane pumps:

Vane Dynamic

Chamber filling

– Piston pumps

Valve plate design model

Lumped parameter CV approach

–2




3

Vane

Pump

Piston Pump

Spool Valve

Gerotor

Pump

Numerical modeling simulations: 1D and 3D CFD approaches



Pumps: experimental setup

Lubrication

Pumps

Pressure ripple

Flow-rate

Torque

Cavitation phenomenon 0 60 120 180 240 300 360Angle [Deg]

0.76

0.8

0.84

0.88

0.92

0.96

1

No

rma

lize

d p

ressu

re

2000rpm-3bar


4



Valves: experimental setup

Hydraulic

valves

Pressure

Flow-rate

Cavitation phenomenon


5



Vane Pumps

Vane dynamic

Main Chamber

MC

Leading Vane

Trailing Vane

6

5

10

15

20

25

30

35

40

45

50

55

60

65

70

75

80

85

0

50

100

150

200

250

300

350

400

0 30 60 90 120 150 180 210 240

Tip

gap

[μm

]

Pre

ssu

re [b

arA

]

Angle [deg]

Main Chamber Pressure Main Chamber Pressure NO DYN.

Leading vane tip gap Trailing vane tip gap



Vane Pumps

Vane dynamic

𝐹𝑡 = 𝐹𝑝 + 𝐹𝑐 + 𝐹𝑓

The contact force for each vane can be evaluated using the following equation:

Where:

• 𝐹𝑝 = 𝑝𝑟,𝑢𝑣 ∙ 𝐴𝑢𝑣 − 𝑝𝑟,𝑡𝑣 ∙ 𝐴𝑡𝑣

• 𝐹𝑐 = 𝑚𝑣 ∙ 𝜔2 𝜌 −𝑙𝑣

2The vector ray 𝜌 is: 𝜌 = 𝑒2 + 𝑅𝑆

2 + 𝑒𝑅𝑠 cos 𝜑 + 𝛿

-200

0

200

400

600

800

1000

1200

1400

1600

1800

2000

2200

2400

0 30 60 90 120 150 180 210 240 270 300 330 360

Forc

e [N

]

Angle [deg]

Bottom Force Tip Force Contact Force

7



-1200

-700

-200

300

800

1300

1800

2300

0 60 120 180 240 300 360

Forc

e [N

]

Angle [deg]

Contact force Vane tip - Stator ring

v0.00 v1.00 v1.01 v1.02

v1.00 v1.01 v1.02

Vane Pumps

Vane dynamic

To cut the forceChange timing, using a groove in reverse

The pressure in the UV increases too slow

Pressure spike in MC

v0.00

8



Vane Pumps

Vane dynamic

70

75

80

85

90

95

45 60 75 90 105 120 135 150 165 180

Inst

anta

ne

ou

s fl

ow

[L/m

in]

Angle [deg]v0.00 v1.00 v1.01 v1.02

9



Vane Pumps

Chamber filling

80

85

90

95

100

105

110

260 270 280 290 300 310 320 330 340 350 360

Inst

anta

ne

ou

s Fl

ow

[L/m

in]

Angle [deg]

Pump - No Vane Dyn. Pump - Vane Dyn. Pump - Vane Dyn. - One Suction

10



Vane Pumps

Chamber filling

0

100

200

300

400

500

600

700

800

900

0

0,1

0,2

0,3

0,4

0,5

0,6

0,7

0,8

0,9

0 45 90 135 180 225 270 315 360

den

sity

[kg

/m3

]

Tota

l gas

vol

ume

frac

tion

[-]

MC angle [deg]

Pump - Two Suctions Pump - One Suction Pump - Two Suctions (Density) Pump - One Suction (Density)

11



Different vane types:

Hydrodynamic Load Capacity

Vane Pumps: Future Works

Vane tip profile

12



• Each control volume CV has homogeneous properties, such as pressure and temperature;

• CV is a capacitive element, it calculates the pressure as function of the net ingoing flow rate;

• CVs are connected by resistive components (variable orifices), calculating flow rate as function of the pressure

drop.

𝑑𝑝𝑖𝑑𝑡

=𝛽

𝑉𝑖𝑄𝑖 − 𝑄𝑠𝑠𝑖 − 𝑄𝑝𝑠𝑖 − 𝑄𝑝𝑐𝑖 − 𝑄𝑣𝑝𝑖 −

𝑑𝑉𝑖𝑑𝑡

Control volumeQpciQpsiQssi

Qvpi

pi

Swashplate

Slipper Piston CylinderBlock

Valve Plate

) () (

Low Pressure source

High Pressure source

𝑄𝐻𝑃𝑖 = 𝑐𝑑𝐴𝐻𝑃𝑖2 𝑝𝑖 − 𝑝𝐻𝑃

𝜌

𝑄𝐿𝑃𝑖 = 𝑐𝑑𝐴𝐿𝑃𝑖2 𝑝𝑖 − 𝑝𝐿𝑃

𝜌

𝑄𝑖 = 𝑄𝐿𝑃𝑖 + 𝑄𝐻𝑃𝑖

Lumped parameter – Control volume approach

• The approach is consisting of two simulations:

1. Valve plate Design, where the valve plate sectional areas are evaluated: the outputs of this model

(tables) become inputs for the following model;

2. Vectorial piston pump, modeled according to the CV approach

Piston Pumps

13



Kidney

Supercomponent

Groove

Supercomponent

The model has two main supercomponents:

• Groove SC, to evaluate the slots;

• Kidney SC, to evaluate the kidneys opening areas.

1 – Valve plate design model

Angular position

of cylinder

Hydraulic diameter

of turbulent orifice

Area


Angular position

of cylinder

Hydraulic diameter


Area


Piston Pumps

14



Real Parameters:

1. Pitch radius

2. Barrel footprint angular extension

3. Barrel slot radius

4. Kidney radius

5. Kidney opening angle

6. Kidney closing angle

1. Pitch radius

2. Barrel footprint angular extension

3. Barrel slot radius

4. Hole radius

5. Hole opening angle

6. Hole closing angle

7. Slot starting height

8. Slot slope

9. Slot angle design (triangular slot)


Piston Pumps

15



Barrel

footprint


Hole area:

In red the

area

evaluated

by the

Groove SC

Limited by:

Piston Pumps

16



Slot area: the slope angle is considered


Kidney area and its limit (barrel footprint area):

Piston Pumps

17



High pressure side

Low pressure side

Portplate model overview

Po

rtp

late

to m

od

el

Example of modeling:


Piston Pumps

18




Example of modeling:

Piston Pumps

19



Displacement chambers

Pressure and volumes

Swashplate dynamics

Forces and torques

Valveplate passageway

Area and hydraulic diam Dh

Volumetric

losses

2 – Lumped parameter CV approach

Piston Pumps

20



The approach is validated comparing the

results with a CFD simulation:

Here is showed a comparison on a pressure

ripple:

Pressure monitoring point (CFD3D)

Approach validation

Piston Pumps

21

West Lafayette June 4th, 2019

FPRG – FLUID POWER RESEARCH GROUP

22

Emma FrosinaAssistant Professor

Department of Industrial Engineering

University of Naples, Italy

[email protected]

mailto:[email protected]

NUMERICAL AND EXPERIMENTAL ANALYSES OF VANE AND … Frosina.pdfNumerical and experimental analyses...

Documents

Transcript of NUMERICAL AND EXPERIMENTAL ANALYSES OF VANE AND … Frosina.pdfNumerical and experimental analyses...