Sizing Accumulators
Basic Accumulator Terms
p0 = gas precharge pressure
V0 = effective gas volume of the accumulator
T0 = temperature at precharging
p1 = minimum working pressure
V1 = gas volume at p1
T1 = minimum ambient temperature
p2 = maximum working pressure
V2 = gas volume at p2
T2 = maximum ambient temperature
(this an internal net volume)
p0 @T0 = gas precharge pressure at precharge ambient temperature
p0 @T1 = gas precharge pressure at minimum ambient temperature
p0 @T2 = gas precharge pressure at maximum ambient temperature
Accumulator Operational Sequence Steps
Bladder
Diaphragm
Piston
1 The bladder accumulator is precharged with
nitrogen to system design specified precharge
pressure prior to accumulator installation.
1 The diaphragm accumulator is precharged
with nitrogen to system design specified
precharge pressure prior to accumulator
installation.
1 The Piston accumulator is precharged with
nitrogen to system design specified precharge
pressure prior to accumulator installation.
• The expanded, pressurized bladder
causes the fluid port poppet to close,
preventing the bladder from extruding
into the fluid port.
• No fluid is inside the accumulator at this
step until the accumulator is installed
in the hydraulic system and the system
pressure becomes greater than the
precharge pressure, P0.
• Once the system working fluid pressure
becomes greater than P0, the poppet
will open and the bladder will begin to
compress.
2 The accumulator is installed in the hydraulic
system and the fluid is increased to the
maximum working system pressure, P2. This is
often called “charging” the accumulator.
• At P2, the gas volume in the bladder
accumulator is V2.
• At this step the maximum amount of fluid
possible for a particular system pressure
range is inside the accumulator and the
fluid is compressing the bladder and
nitrogen gas to smallest gas volume.
3 During operation, the minimum working
system pressure, P1, is reached and the
gas volume is now V1. This is often called
“discharging” the accumulator.
• V1 is the maximum gas volume during
hydraulic system operation and correlates
to the smallest possible fluid volume
inside the accumulator during system
operation.
• The amount of fluid that is expelled, or
supplied, to the hydraulic system is ∆V,
where ∆V = V1 - V2
• A small amount of fluid should remain
inside the accumulator at P1, in order
to prevent the bladder from rubbing or
chaffing against the fluid port poppet
which will cause bladder damage.
• Therefore the precharge pressure, P0,
should always be slightly lower than the
minimum working system pressure, P1.
92
• The expanded, pressurized diaphragm
causes the integral poppet in the
diaphragm to close over the fluid port
opening, preventing the diaphragm from
extruding into the fluid port.
• No fluid is inside the accumulator at this
step until the accumulator is installed
in the hydraulic system and the system
pressure becomes greater than the
precharge pressure, P0.
• Once the system working fluid pressure
becomes greater than P0, the diaphragm
with an integrated poppet, will begin to
compress and cause the integral poppet
to move away from the fluid port opening.
2 The accumulator is installed in the hydraulic
system and the fluid is increased to the
maximum working system pressure, P2. This is
often called “charging” the accumulator.
• At P2, the gas volume in the diaphragm
accumulator is V2.
• At this step the maximum amount of fluid
possible for a particular system pressure
range is inside the accumulator and the
fluid is compressing the diaphragm and
nitrogen gas to smallest gas volume.
3 During operation, the minimum working
system pressure, P1, is reached and the
gas volume is now V1. This is often called
“discharging” the accumulator.
• P1 is the maximum gas volume during
hydraulic system operation and correlates
to the smallest possible fluid volume
inside the accumulator during system
operation.
• The amount of fluid that is expelled, or
supplied, to the hydraulic system is ∆V,
where ∆V = V1 - V2
• A small amount of fluid should remain
inside the accumulator at P1, in order to
prevent the diaphragm from rubbing or
chaffing against the shell which will cause
diaphragm damage.
• Therefore the precharge pressure, P0,
should always be slightly lower than the
minimum working system pressure, P1.
INNOVATIVE FLUID POWER
• The pressurized nitrogen will cause the
piston to move completely over to the
fluid port side.
• No fluid is inside the accumulator at this
step until the accumulator is installed
in the hydraulic system and the system
pressure becomes greater than the
precharge pressure, P0.
• Once the system working fluid pressure
becomes greater than P0, the fluid
pressure will begin to compress the gas
by overcoming the precharge pressure,
and cause piston to move away from the
fluid port opening.
2 The accumulator is installed in the hydraulic
system and the fluid is increased to the
maximum working system pressure, P2. This is
often called “charging” the accumulator.
• At P2, the gas volume in the piston
accumulator is V2.
• At this step the maximum amount of fluid
possible for a particular system pressure
range is inside the accumulator and the
fluid is exerting force on the piston and
compressing nitrogen gas to the smallest
gas volume.
3 During operation, the minimum working
system pressure, P1, is reached and the
gas volume is now V1. This is often called
“discharging” the accumulator.
• P1 is the maximum gas volume during
hydraulic system operation and correlates
to the smallest possible fluid volume
inside the accumulator during system
operation.
• The amount of fluid that is expelled, or
supplied, to the hydraulic system is ∆V,
where ∆V = V1 - V2
• A small amount of fluid should remain
inside the accumulator at P1, in order to
prevent the piston from impacting the end
cap for any system cycle.
• Therefore the precharge pressure, P0,
should always be slightly lower than the
minimum working system pressure, P1.
PN#02068195 / 04.13 / ACU1102-1326
Sizing Accumulators
Accumulators
Bladder
Diaphragm
Piston
Precharge Recommendations
For energy storage:
For shock absorption:
For pulsation dampening:
p0 = 0.9 x p1
p0 = (0.6 to 0.9) x pm
p0 = (0.6 to 0.8) x pm
p1 = minimum working pressure
pm = median working pressure at free flow
pm = median working pressure
Temperature Effect
Due to the Ideal Gas Laws, the precharge pressure of an accumulator is affected by the ambient temperature of the accumulator’s operating
environment. Given the constant volume of an accumulator shell when the temperature rises, the gas pressure will increase and conversely
as the temperature goes lower, the gas pressure decreases. This temperature effect on precharge gas pressure will affect operation of the
accumulator in a hydraulic fluid system. Therefore it is critical to consider the precharge pressure at T2, maximum ambient temperature, and T1,
the minimum ambient temperature, when sizing an accumulator to ensure that the accumulator is sized large enough to operate properly over the
entire operating ambient temperature range. The formula below describes the ambient temperature and precharge pressure relationship to any
temperature. Refer to the sizing example on page 95 to see how the formula is applied in the sizing calculation process.
Fahrenheit
p0 @T0
= p0 @Tx x
T0
(
T0 + 460
Tx + 460
)
= precharge temperature in °F
Celsius
p0 @T0
= p0 @Tx x
T0
(
T0 + 273
Tx + 273
)
= precharge temperature in °C
= actual ambient operating temperature in °F, where Tx is
Tx
T1 ≤ Tx ≤ T2
= maximum operating temperature in °C, where Tx is
Tx T1 ≤ Tx ≤ T2
p0 @T0
=gas precharge pressure at precharge ambient
temperature
p0 @T0
=gas precharge pressure at precharge ambient
temperature
p0 @Tx
=gas precharge pressure at maximum ambient operating
temperature, where Tx is T1 ≤ Tx ≤ T2
p0 @T2
=gas precharge pressure at maximum ambient operating
temperature, where Tx is T1 ≤ Tx ≤ T2
PN#02068195 / 04.13 / ACU1102-1326
INNOVATIVE FLUID POWER
93
Sizing Accumulators
Gas Behavior
su
es
correction factor Ci
correction factor Ca
( ) ( () ) (
( ) ( )
( )
(( )) ((
( ) ( )
( )
( ) (
( ) ( )
( ) ( )
(
)
(
)
(
)
(
)
(
)
(
)
pr
( )
( ) ( )
( ) ( )
( ) ( )
( ) ( )
( ) ( )
( ) ( )
( ) ( )
( ) ( )
g
kin
or
xw
ma
( )
ng
ki
or
xw
ma
The compression and expansion processes
Determine the following:
Correction factor Ci Isothermal
taking place in hydro-pneumatic accumulators
change of condition
are governed by the general gas laws.
Necessary accumulator size, taking into
The following applies for ideal gases:
account the real gas behavior by using
1.7
correction factors
p 0 x V0n = p1 x V1n = p2 x V2n
1.6
Calculate gas precharge pressure p0 at 68°F
where the time related change of state is
represented by the polytropic exponent “n”.
(T0 )
For slow gas expansion and compression
1.5
Select
accumulator size and type
processes which occur almost isothermically,
the polytropic exponent can be assumed to
Solution:
1.4
be n = 1.
Since it is a rapid process, the change of
pr
For rapid processes, the adiabatic change of
es
1.3
condition of the gas can be assumed to be
su
re
state can be calculated using n = k = 1.4 (for
p2
adiabatic.
=4
nitrogen as a diatomic gas)
00
1.2
ba
r
1. Calculation for the required ideal gas volume:
(58
For pressures above 3000 psi the real gas
30
00 p
0b
si)
ar (
behavior deviates considerably from the ideal
4
a) gas precharge pressure at T2:
1.1
350
200
psi)
one, which reduces the effective fluid volume
b ar
(2900 p
s
i
)
p0 @T2 = 0.9 x p1 = 0.9 x 1500 = 1350 psi
∆V. In such cases a correction is made which
1.0
takes into account an adiabatic exponent (k)
1
2
3
4
5
b) gas precharge pressure at T1:
even greater than 1.4; n = k > 1.4. By using the
pressure ratio p2/p1
T1 + 460
following formulas, the required gas volume V0
p0 @T1 = p0 @ T2 x
can be calculated for various calculations.
T2 + 460
Correction factor Ca Adiabatic
For low pressure applications of less than 150
75 + 460
psi absolute gas pressures must always be
change of condition
= 1245 psi
p0 @T1 =
1350 psi x
used in the formulas.
120
+ 460
∆V
1.7
V0 =
∆V
∆V
c) ideal gas volume:
V0 =
p0 1/n
p0 1/n
V0 = 1/n
∆V
1.6
1/n ∆V
∆V
0.714
0.714 V0,
P 0 p , (T )
P0
p1
p2
=
p
,
(
T
)
V
=
ideal
0
1
0
1
0
V0 =
∆V
0.714
P1p 1/n
P2p p1/n
∆V
P0@(T1) 0.714
Calculation Formulas
p2
V0 idealV0 =P0@(T1)
1.5
0
0
p0 1/n
p0 1/n
V
=1
0
P
1
P
p1
p2
p0, (T1) 0.714
p02, (T1) 0.714
p1∆V
p2
p0, (T1) 0.714
p0, (T1) 0.714
re
1.4
p1
p2
p2
V0 =
p1 15∆V
p2
polytropic:
=
40
∆V
p0 1/n
p0 1/n
0b
V=0 =
1.35
V
a
∆V
V0 =
0
r(
1.3
0.714
0.714
30
p1
p2
p0, (T1)0.714
p508, 0(0T1) 0.714
V0Videal
=
= 3.95 gals.
0,ideal =
0 b 1150
V0 =
1150
p0
p0
ps
15
ar
i)
∆V
p
p
(
15
1245 0.714
1245 0.714
4
2
350 1
0
P
0
P
1500
3000
p1
p2 ∆V
V
=
2
1.2 V0 =
0
00 V = psi
)
V0 =
1500
3000
b ar 0
Pp1 P2 p
isothermal:
1150 0.714
1150 0.714
(290
0.714
0
0
1150 0.714
0 ps1150
p0
p0
i)
1500
3000
1.1
p
p
(n=1)
1
2
1500 15
3000
p
p2
∆V
2. Calculation for the required real gas volume:
1
V0 =
V0 =
∆V
0.714
1.0
a) Determine the adiabatic correction factor, Ca
1150
1150 0.714
p0
∆V2
V 0 = p0
1
3
4
5
adiabatic:
0.714
0.714
p2
3000psi
1500
3000
V0 =
pp1 0
p2
p0
=
=2
0.714 ∆V ratio0.714
pressure
p2/p1
(n = k = 1.4)
0
P
0
P
p1
p∆V
1500psi
p1
V0 =
2
V0 =
P1p 0.714 P2p 0.714
0
0
From the correction factor for adiabatic
p0 0.714
p0 0.714Sizing Example
p1
p2
Correction factors to take into account
change condition graph, using the 3000psi
p1 ∆V the preal
2
T
+
460
An additional operation is 0to be added to an
gas behavior(2
T0 + 460
curve:
V0 =
T2 + 460 1.35 gallons
p0 0.714
p0 0.714 existing machine which requires
For isothermal change of condition:
+460
460
CTa2T≈+0 1.16
of
oil
in
2.5
seconds
for
optimal
operation.
The
T0 + 460
p1
p2
T
+ 460
V0,real = Ci x V0,ideal or
2
system must operate betweenT3000
psi and
b)
Real
gas
volume:
+
460
2
+ 460
1500 psi. The operating 68
ambient
temperature
∆V0,real = ∆Videal
68
x+V460
=1.16 x 3.95 gal.
V0, real = C
140
+ 460 hydraulic
a
0, ideal
range is 75 to 120°F. The
machine’s
T0 + 460
120
460
Ci
68++gal.
460
=
4.6
fluid pump is sufficient to fully
recharge
the
T2 +68
460
+ 460
140 + 460
accumulator in the 8 second machine
dwell
for adiabatic change of condition:
3. Select actual accumulator size by rounding
140 + 460
time. Total machine cycle time = 10.5s.
up to nearest nominal size accumulator
V0,real = Ca x V0,ideal or
listed in catalog:
68 + 460
Given:
∆Vreal = ∆ V0,ideal
+ 460
Selected size: 5 Gallon = 20 Liter
maximum system working140
pressure
Ca
p2 = 3000 psi
The Ci and Ca can be determined from the folminimum system working pressure
4. Calculation of gas precharge
lowing Correction factor graphs.
p1 = 1500 psi
pressure p0 at 68°F:
Calculate the ratio of Max/Min pressure, p2 /p1.
required fluid volume of the system
p 0 @ T0 = p 0 @ T 2 x
On the graph find the intersection of p2 /p1 and
T0 + 460
∆V = 1.35 gallons
the maximum working system pressure p2,
= 1350 psi x
T2 + 460
which is shown as a curve on the graphs for
maximum ambient operating temperature
= 1230 psi
either an isothermal or adiabatic change of
T2 = 120°F
condition.
3. Selected: Size 20 (5 gallon)
minimum ambient operating temperature
Project the intersection point to the Y-axis to
T
=
75°F
Recommended Model: SB330-20A1/112S1
determine the appropriate correction factor,
210C, Precharged to 1230 psi at 68°F
C or C
)
(
)
(
))
(
(
(
(
)
)
(
)
)
)
(
(
94
)
)
)
)
)
(
(
(
(
)
)
)
)
(
i
(
)
a.
INNOVATIVE FLUID POWER
PN#02068195 / 04.13 / ACU1102-1326
Sizing Accumulators
Pulsation Dampeners & Suction Flow Stabilizers
On the suction and pressure side of piston pumps almost identical
conditions regarding non-uniformity of the flow rate occur. Therefore
the same formulas for determining the effective gas volume are used
for calculating the dampener size. That in the end two totally different
dampener types are used is due to the different acceleration and
pressure ratios on the two sides.
V0
V0
Not only is the gas volume V0 a decisive factor but also the
connection size of the pump has to be taken into account when
selecting the pulsation dampener. In order to avoid additional cross
section changes which represent reflection points for vibrations, and
also to keep pressure drops to a reasonable level, the connection
cross section of the dampener has to be the same as the pipe line.
The gas volume V0 of the dampener is determined with the aid of the
formula for adiabatic changes of state.
A simulation of the pressure performance can be carried out by
means of a computer program for real pipe line conditions.
V
V0 (l) =
100 0.714
0.695 x 1 Formulas
100 + x
100
0.695 x 1100
100 + x
1-
X (±%) =
1∆V (l) =
X (±%) =
V
0.695 x V0
100
1.4
V
0.695 x V0
1.4
0.714
- 100
- 100
pˆ - pm
pm
V
V0 (in3) =
100 0.714
0.695
Types of
Pump1 - 100 + X z
Gear Pump
7 - 14
V
3
V0 (in
) = Pump
2
2.36
x
π
Piston
- 11
0.13
3.15
100 10.714
4
0.695
1
3
e.g.
V0 (in ) =
100 + X 1
0.714
100
2
0.695 1 100 +2 2.5
3
0.13 2.36 x π 3.15
4
3
4
V0 (in ) =
0.714
100
5
0.695 1 100 + 2.5 6
V
0.695 1 -
x 100 =
p - pm
pm
p̂ - pm = p̆ - pm = amplitude of pressure fluctuations
V
V0 (l) =
X
= residual pulsations
100
p̂ = max. working pressure 0.695 x 1 - 100 + x
p̆ = min. working pressure
100
100 + X
k
0.1 - 0.3
0.01 - 0.6
0.6
0.25
0.13
0.12
0.05
0.13
7
0.02
0.714
9
0.01
Calculation Example
x 100
= required gas volume
pˆ - pm
p - pm
x 100 =
x 100
X (±%) =
∆V = fluctuating fluid p
volume
pm
m
q(l) = stroke volume per cylinder
V0
pressure side
V0 (in3) =
kq
ˆ
X (±%) =
∆V
ˆ
V0 (l) =
suction side
0.714
V
Parameters:
V0 (in3) =
2.362 x π 0.714
0.13
3.15
100
Single 3acting
3-plunger
4
0.695
1 - pump
V
(in
)
=
100
+
X
0
piston diameter
2.36 inches
0.714
100
piston stroke
3.15
0.695 1 100 +2 0.5
x π 3.15
rpm
0.13 2.36 370
464.44 gpm
3
flow
rate
V0 (in
)=
operating temp.
68°F 0.714
100
V
0.695
1
3
operating pressure
V0 (in ) = 100 + 0.5
pressure side
3625 psi 100
0.695 1 suction side
58 psi 100 + X
(60 mm)
(80 mm)
(244 l/min.)
(20°C)
0.714
(250 bar)
(4 bar)
Required: 1
2
2.36
xpulsation
π 3.15of ± 2.5%
V
•
Suction
stabilizer 0.13
for a residual
3
1Vflow
D
(in
)
=
4
0
3
p x Vx0dampener
)=
0.714 of 0.5%
•
Pulsation
for a residual
pulsation
K E(inx e
100
0.714
100
0.695 1 0.695 1 - 100 + X
Solution: 1
100 + 2.5
a) Determination of required
1 suction flow stabilizer
1
D
2.362 x π 3.15
px
x 1
0.13 250
K Exe
980
x
x
9
3 10
100
2.04 x 1011 4x 6.3
V1.62
)=
0 (in x
X (±%) =
- 100
0.714
100
1.4
V
1
P
0.695
11100
+
2.5
V
(bar)
0.695 x V0
3
250
V (in1
)=
1
980 SB
x 0330-4 (see
0.714
Selected:
onx page
13)
9 xtable
11100
2
1.62
x
10
2.04
10
xp 6.3
0.714
m x v x0.695
0.4 1 p
1
D
x100p+1 X
0.286
p x pxˆ - p
0
p2required
pm
p - pm
K E xme
b) Determination
dampener
2 x p1 x of
- 1 pulsation
x 102
x 100 =
x 100
X (±%) =
p1
2
p
1 pm
2.36
xπ
pm
V
p1 0.714 3.15
m 33x) =
v2 x 0.40.13
V0 (in
4
1
D
x 100
V0 (in ) =
0.714
p
0.714
px
x
p2 0.286
t (sec)
0.252 x π
0.695
110
- 2 1000
K2 E x e
2
x
p
x
1
x
980
x
x
2000
x
2.452
0.4
0.714
100
+
X
0.695
1
0.714
m x v x 0.4
1
p
p
7
100
+
0.5
1
4
pˆ - pm
x 1 p - pm
x
V0 (l) =
0.286
4.5 61)
x2 100p=0
x 100
X (±%)
=
p1 0.286
11
Selected:
SB
330
P-20
(see table
on page
2
2
2 x p1 x
-1pmx 10
2
x
7
x
1
x
10
2.36
x π 3.15
p
m
p0
0.13
7
0.252 x π
4
3
Vx0 (in
) =x 2.452 x 0.4
For assistance in sizing pulsationmdampeners,
2000
x v2 x 0.4shock absorbers,
p 0.714 and suction stabilizers,980 x
7 0.714
0.714
4
please contact
HYDAC.
x 1
x 100
V0 (l) =the HYDAC Accumulator Group at 1-877-GO
0.695
1
p
0.286
0.286
4.5
0
p1
11
100
+
0.5
2
2 x p1 x
-1 x 10
2x7x
- 1 x 102
p0
7
PN#02068195 / 04.13 / ACU1102-1326
1
pm = pump flow rate or pressure in the suction line
V
V0 (l) =
100
= Coefficient of cyclic
variation of the
pump
X (±%) =
100
100 -0.714
1.4
0.695 x cylinders
1V
z
=No. of compressions / effective
per
100
+ x revolution
1
factors for other types, i.e. gear,
axial,
0.695
x and
V0 radial piston
pumps on request
ˆ
ˆ
INNOVATIVE FLUID POWER
px
1
D
x
K Exe
95
Sizing Accumulators
Energy Storage Form
Name
Title
Company
E-mail
Address
Phone
State
Phone
Fax
Zip
Please attach any special requirements or drawings to the fax or e-mail.
Operation of Pump
Continuous Operation
Emergency Operation
Maximum Operating Pressure
(P2)
PSI
Minimum Operating Pressure
(P1)
PSI
Precharge Pressure at 68˚F (20˚C)
(P0)
PSI
Temperature Range of Environment
(T)
˚F
Temperature Range of Fluid or System
(TF)
˚F
Pump Flow Rate
(QP)
GPM
Total Cycle Time of System
(TE)
Sec.
Number of Actuators (cylinders, etc.)
(NV)
Actuator Time Schedule and Flow
QVi = Required Actuator Flow (GPM)
Ei = Actuator Start Time
Ai = Actuator Shut Down Time
(i = 1 for first actuator, i = 2 for second actuator, etc. up to NV)
QV1 =
E1 =
A1 =
QV2 =
E2 =
A2 =
QV3 =
E3 =
A3 =
QV4 =
E4 =
A4 =
QV5 =
E5 =
A5 =
Fluid
Required Mounting Orientation
Country of Final Installation (for country codes please see page 2)
Required Quantity
Annual Usage
Target Price
Competitor
Quantity
Additional Remarks
96
INNOVATIVE FLUID POWER
PN#02068195 / 04.13 / ACU1102-1326
Sizing Accumulators
Shock Applications Form
Name
Title
Company
E-mail
Address
Phone
State
Phone
Fax
Zip
Please attach any special requirements or drawings to the fax or e-mail.
What is the source of the shock? (i.e. valve closing, pump start, or other - please describe)
At the instance the shock occurs what is the...
Flow rate:
GPM
Normal Operating Pressure:
PSI ; Maximum Spike Pressure:
The system’s maximum allowable design pressure:
PSI
PSI
Information is required on all piping from the shock source to the anticipated location of the shock absorber (accumulator) .
Please continue to answer the following:
Total Number of pipes:
(up to 10 pipes)
Starting at the shock source, please answer the following:
Pipe
Inner
Length
Diameter
Pipe
(feet)
(inches)
1
6
2
7
3
8
4
9
5
10
Inner
Diameter
(inches)
Length
(feet)
If the vertical height from the shock source to the anticipated location of the shock absorber is greater than 10 feet
please state this distance.
Vertical Height:
feet
Fluid
Required Mounting Orientation
Country of Final Installation (for country codes please see page 2)
Required Quantity
Annual Usage
Target Price
Competitor
Quantity
Additional Remarks
PN#02068195 / 04.13 / ACU1102-1326
INNOVATIVE FLUID POWER
97
Sizing Accumulators
Pulsation Dampening Form
Name
Title
Company
E-mail
Address
Phone
State
Phone
Fax
Zip
Please attach any special requirements or drawings to the fax or e-mail.
What type of pump is causing the pulsation?
Please name or describe (ie piston pump, gear pump, etc.)
What is the...
Flow rate:
Pump:
GPM
RPM
Pump Piston Diameter:
(inches)
Pump Piston Stoke:
(inches)
Number of Rotating Elements:
Operating Pressure:
(3 piston, 13 tooth gear, etc)
psi
The system’s maximum allowable pressure:
psi
Line Size where pulsation dampener will be fitted into:
(The I.D. of the line is what is really required)
Note: A pulsation dampener should be always be installed as close to the pulsation source as possible to optimize its performance. A pulsation dampener
should never be placed greater than 10 ft away from the pulsation source.
Fluid
Required Mounting Orientation
Country of Final Installation (for country codes please see page 2)
Required Quantity
Annual Usage
Target Price
Competitor
Quantity
Additional Remarks
98
INNOVATIVE FLUID POWER
PN#02068195 / 04.13 / ACU1102-1326