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GA
(expended) PhydrmechP
PW
M Q , p MF, v
, ,
QUALITATIVE APPROACH: FUNCTIONAL ANALYSIS
QUANTITATIVE APPROACH: NUMERICAL MODELS
GRC
WP
Q , p
Phydr
GU
WP
Date
File nametraen_eng
21 Dec 2017
ENERGY CONVERSION IN A FLUID POWER SYSTEM
PRIMEMOVER(electric motor,IC engine)
LOAD
GA: FLOW GENERATING GROUPGRC: CONTROL GROUPGU: USERS GROUP
PW
fluid leakages
mechanical friction
pressure drops
WASTED POWER(heat flow rate)
rotary shaftoil pipes oil pipes rotary shafts,
translating rods
Pmech(useful)
overall systemefficiency
Q: volumetric flow rate (L/min)p: gauge pressure (bar) - p = 0 --> atmospheric pressureM: torque (Nm) : angular speed (rad/s) / n (rev/min)F: force (N)v: linear speed (m/s)
7 Reprint 2018
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Date
File nameGA_GRC_GU_eng
09 Nov 2015
GA - GRC - GU
- pump(converts shaft speed into a volumetric flowrate by displacing trapped volumes of fluid)- reservoir (p = 0)- filter & heat exchanger- ...
valves:- to prevent / allow fluid flow- to direct selectively fluid- to limit / reduce a pressure- to control a flow rate (actuator speed)- ...
- linear actuators- hydraulic motors(convert volumetric flow rateinto shaft angular speed orrod linear speed)
application for printing cylinder positioning
supply line(high pressure)
return line(lowpressure)
control signal
manual electric hydraulic mechanical
directional control valve, manual operated
GA
GRC GU
pump
F, M pv,Q
motor
... and what about the fluid pressure ?
ONLY IF a flow rate meetsresistance a pressure is induced
In synthesis
8 Reprint 2018
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Date
File namenormintr0_eng
01 Feb 2018
YES NO
graphic representation of the model of a fluid power component or system
THE LANGUAGE OF FLUID POWER
function
operation
connections
manufacturing
dimensions
installation
GENERAL RULES: components are created using the basic symbols, taking into account the rules given for their creation symbols show the rest position of a component all ports (external connections) of a symbol must be shown basic symbols can be rotated (with increments of 90°) or mirrored to create components components must be represented in the same scale (relative size must be preserved)
International Standard ISO 1219/1-91(latest version 1219/1-2012)
9 Reprint 2018
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M,
A
B
P
T
GA GRC
p*
S
in regulating condition
FUNCTIONAL ANALYSIS: plant schematic according to ISO-1219
F,v
GU
Date
File namescstart_eng2
10 Feb 2018
M,
displacement
surface on which theinlet pp pressure acts
pilot line (transferspressure information)
Equations for pump and hydraulic motor (ideal)
drain line: return to thereservoir the fluid lostdue to the internalclearances
spring exerting a closingforce Fspr that can bemodified by the user
filter
unidirectional restrictor
reservoir
primemover(electricmotor)
pump
double acting linear actuator
hydraulic motor(two directions of flow)
D4/3
heat exchanger
pressure relief valve
10 Reprint 2018
Preview
A
B
P
T
GRC
v
A
a
D
d F
A
B
P
T x
FUNCTIONAL ANALYSIS: plant schematic according to ISO-1219
F,v
GU
Date
File namescstart_eng3
09 Feb 2018
four-port three-positiondirection control valveclosed centre,solenoid actuated,spring centered
D = piston diameterd = rod diameter
equilibrium on the piston(steady-state)
the ingoing volume of fluid per unit time (Q)must be equal to the increment per unit timeof the chamber volume (incompressible fluid)
valid also for the outlet side:
position at rest(no command)
free flow(ideally p = p )
restricted flow(p > p )
1 2
1 2
12
restriction of the flowarea: the degree ofthrottling is decidedby the user
11 Reprint 2018
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Date
File namefc1a30_eng
15 Nov 2015
DUAL STAGE PRESSURE RELIEF VALVE (FLUID CONTROL 1A30)
SPOOL TYPE - CARTRIDGE CONSTRUCTION
P
T
fspr
p*S1
S2
SPOOL (MAIN STAGE) BALL POPPET (PILOT STAGE)
FUNCTIONALRESTRICTOR S1
DYNAMIC RESTRICTOR S2
INTERNAL DRAIN
96 Reprint 2018
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limpprop_eng
08 Jan 2018
PROPORTIONAL PRESSURE RELIEF VALVE (Denison R4VP)
P T
G
G
X Y
YX
Date
File name
mechanical pilot stage (safety)
main stage
proportional pilot stage
solenoid
LVDT
p*1
p*2
fm
S
97 Reprint 2018
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Date
File namesimVL1
08 Jan 2018
SIMULATION OF A DUAL STAGE RELIEF VALVE
S1
S2
PUMP FLOW RATE = 150 L/minD spool = 10 mmfspr = 30 Ndiameter S1 = 1 mm
S2 S1
p*
p* = 45 bar
fspr
restrictor (load)
98 Reprint 2018
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Date
File namesimVL2
18 Jan 2017
SIMULATION OF A DUAL STAGE RELIEF VALVE
p* main stage = 51.5 bar max pressure = 52.4 bar
p* pilot stage FORCES ON THE MAIN STAGE
p* pilot stage main stage p*
fspr / S = 3.8 bar
99 Reprint 2018
Preview
Date
File namegumdevcb_eng
08 Jan 2018
RV2
VSH
p
p
GAQF (p*)
p*
1
2
2
21
A
a
VCBVCBsprF
J1J2
J3 J4
NR3NR2
J5
J7 J8
J6
J9NR1
J10
(p* )VCB
2 1
v FvF
CONTROL OF OVERRUNNING LOADS WITH "COUNTERBALANCE" VALVES
overrunning load resistant load
resistant load
overrunning load
STUDY HYPOTHESES position D2 (outward stroke) ---> flow through VCB2 resistant and overrunning loads
Remarks: leak tight conditions attained through poppet design. Spools
are not leak proof! By-pass centre of DCV to avoid spurious pilot signals RV2 is necessary to limit the pressure at the actuator outlet
2 equations to determine the pressures p1 and p2 actuator equilibrium VCB2 equilibrium
DCV
S S
sprF
191 Reprint 2018
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p*a
p*2
Ap* a -2p*
p*
2p*
a
v>0
v=0
v<0
p
p
1
2
p
F
2p* a
Ap*
p*A2p* A
F
Q/A
Q/a
v
2
p*VCB
Aa
Date
File namevcbpfvf_new_eng
08 Jan 2018
v FF
in
out
v
resistant load
overrunning load
DVC in D2
position D2
position D1
in
out
STEADY STATE CHARACTERISTIC p-F AND v-F WITH VCB
resistantoverrunning
resistantoverrunning
VCB open2VCB regulates2VCBclosed
2
decreasing flow area
RV
2 re
gula
tes
RV2 regulates
NR3 closed
p*VCB
Ap*VCBAp*
VCB resist.Foverr.
resistant load
192 Reprint 2018
Preview
Date
File namevcb_1cpbd30
19 Jul 2017
VCB VALVE (Integrated Hydraulics 60 1CPBD300)
AB X
Y
A
B
X Y
A
B
X (cross pilot line)
ACTUATOR
DIRECTION CONTROL VALVE
integral NR valve
193 Reprint 2018
Preview
Date
File nameguvcbsez_eng
08 Jan 2018
RV2
GAQF (p*)
p*2
21
A XY
B
PLANT WITH CONTROL OF OVERRUNNING LOAD THROUGH VCB VALVES
D0: load blockedD1: load lowering (overrunning load)D2: load lifting (resistant load)
0
B
AX
F
Note:valves representedin configuration D1
non return valve behaviourVCB behaviour
Kg
194 Reprint 2018
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Date
File namemodcar1_eng
24 Nov 2013
TEST RIG FOR OVERCENTRE VALVES (LOAD TEST RIG)
Primary circuit(hydraulic winch)
Secondary circuit (load)Flywheel
OVCundertest
286 Reprint 2018
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Date
File namemodcar1b_eng
24 Nov 2013
SIMPLIFIED HYDRAULIC SCHEME
br
SE
p*
D2
0
M1 M2p*
VL
LOAD TEST RIG
VL
1
Primary circuit Secondary circuit
PVB 3
s
S
p*
OVC
OVC
VPA 40 LS VPA 20 MS
NR2
01 2
1 2 P T Y
Notice that: VM1 = VM2
PVB3 is mounted on the LS test rig The flow generation unit is located downstairs Qmax PVB 3 < Q VPA 20
PVB3 decides the flow rate throughthe primary circuit
VL and NR2 decide the pressurerespectively in the high and lowpressure lines of the secondary circuit
D2 selects the type of load
287 Reprint 2018
Preview
Date
File namemodcarico_eng
19 May 2015
P1
3A 3B
21
P2 (VPA 20)
0
GA
LS
LS test rig
T
br
SE
p*
D2
0
NR2
St
M1 M2
NR3 NR3
NR3NR3
LOAD TEST RIG
SC
1
Y1 2 P T
Q4
Q 3 Q1Q 2
SE
St
1 2
Q4NR1 NR1
Ap Bpbrakep
1p
2p
Ap Bpbrakep
brp*
M1
VPA20p
Primary circuit Secondary circuit
PVB 3
s
S
p*
OVC
OVC s
S
p*
OVC
OVC
mounting of the OVC withintegral shuttle valve
T
DETAILED SCHEME
p*VL
VL
quick couplings
288 Reprint 2018
Preview
Date
File namemodcaricoall_eng
24 Nov 2013
COMPLETE LAYOUT
Load Sensingtest rig
Flow generating unit(downstairs)
OVC valve test rig
Data acquisition system
PVB 3 joystick
289 Reprint 2018
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