Low cost and high performance screen laminate regenerator matrix.pdf
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Low cost and high performance screen laminate regenerator matrix
Uri Bin-Nun *, Dan Manitakos
FLIR Systems, 16 Esquire Road, North Billerica, MA 01862, USA
Abstract
A laminate screen matrix regenerator with 47 elements has been designed, analyzed, fabricated and tested. The laminate was
fabricated from stainless steel screen sheets that were stacked on top of each other at certain angular orientation and then bonded at
high temperature and pressure environment utilizing a sintering process. This laminate is a porous structure media with highly
repeatable properties that can be controlled by varying mesh size, weave type, wire size and laminate sheet to sheet orientation. The
flow direction in relation to the weave plan can be varied by cutting a cylindrical or rectangular laminate element along or across theweave. The regenerator flow resistance, thermal conductance losses, dead volume, surface area and heat transfer coefficient are
analyzed. Regenerator cost and performance comparison data between the conventional widely used method of stacked screens and
the new stacked laminate matrix regenerator is discussed. Also, a square stainless steel screen laminate was manufactured in a way
which permits gas to flow along the screen wire instead of across it.
2004 Published by Elsevier Ltd.
Keywords: Convection (C); Heat transfer (C); Regenerators (E); Stirling (E); Thermal conductivity (C)
1. The common Stirling cycle regenerator
The common Stirling cycle regenerator is a one way
bidirectional heat exchanger in which thermal energy
flows in and out of the matrix and to or from the
working fluid. The heat exchanging media (matrix) is
usually made of light felt like mass of fine wire stacked
in a well insulated tube as shown in Fig. 1. The fine wire
mesh is commonly obtained in a form of woven screen
at variety of wire sizes, weave structures, mesh density
and materials. Other types of regenerator matrix are
also used such as spheres made of stainless steel, bronze,
lead and erbium to name a few. The common Stirling
cycle regenerator matrix usually has large thermal
capacity, large surface area, low flow impedance, small
void volume and large axial thermal resistance which areall essential to achieving high regenerator effectiveness.
Cooler performance is very sensitive to regenerator
effectiveness. A regenerator is considered 100% effective
when the temperature of the working fluid exiting the
regenerator is equal to the temperature of working fluid
entering it. If the temperature of the gas leaving the
regenerator at the compressor end is colder than the
entering gas it indicates that not enough thermal energy
was remove from the regenerator matrix. This causes the
regenerator to be warmer than it could have been and
thus reducing the pre-cooling of the incoming gas prior
to it entering the expansion space.
2. Screen laminate sintering process
Sintering is the fundamental processing step for all
porous metal products. This means bonding of powder
particles by diffusion process at high pressure and tem-
perature just below the melting point of the sintered
metal. After the sintering process is complete, no phys-
ical limits exist at the boundaries of the original particlesand they become fused at the contact points.
Similarly screen laminate is manufactured by a sin-
tering process in which the powder particles are replaced
with woven stainless steel screen sheets as the base
material. The screen sheets are placed on top of each
other at 45 (any other angle is possible) alternating
angle relative to wire weave direction. The stack of
screens is then placed in an environmental chamber at
high pressure and temperature just below the melting
point. The laminate is kept in this heated and com-
pressed state for a certain period of time until a bond is
* Corresponding author. Tel.: +1-978-901-8242; fax: +1-978-901-
8441.
E-mail address: [email protected] (U. Bin-Nun).
0011-2275/$ - see front matter 2004 Published by Elsevier Ltd.
doi:10.1016/j.cryogenics.2004.03.015
Cryogenics 44 (2004) 439444
www.elsevier.com/locate/cryogenics
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formed at the contact points between the screen wires.
The bonding is achieved by diffusion of material at the
point of contact resulting in a fused solid structure at the
contact boundaries of the screen wires. The screen
laminate is then laser cut, electro discharge machined(EDM), or die cut to form a cylindrical shape. The
cylindrical laminate elements are usually oriented so
that the flow is vertical to weave plan (Fig. 2).
In order to resolve cost and yield issue involving
regenerator manufacturing FLIR SystemsBoston
developed a new regenerator matrix element (Fig. 2) as
described in the following paragraph.
The laminate element can be cut from a thick lami-
nate screen stock, such that the flow axis is parallel or
normal to the weave plan (along the wire axis) as shown
in Fig. 3.
The final parts are solid, rigid and relatively thick
porous structures having more surface area and less
dead volume per unit length than a stack of individual
single screens. The laminate screen element thermal
conductance is much higher than an equivalent stack of
single screen disks causing a larger heat loss along
the regenerator axis. To remedy this problem, the lam-
inate thickness was reduced. This resulted in an increase
of the number of laminate screens and thus increas-
ing thermal contact resistances along the regenera-
tor axis thus reducing heat loss. The final product
thickness was optimized to achieve minimum number of
laminates (Fig. 2) while minimizing heat flow, maxi-
mizing surface area, reducing dead volume and maxi-
mizing rigidity.
3. Refrigeration losses due to regenerator effectiveness
The equation which determines refrigeration loss as a
function expansion ratio V4=V3, temperature ratioT2=T3, specific heat ratio, c Cp=Cv and regeneratoreffectiveness, e is shown below [1].
Nomenclature
e regenerator effectiveness, none
f friction factor, none
dk hydraulic diameter, ft (m)
h matrix convection coefficient, W/in.2 C, (W/
m2 K)oP=oX pressure drop per unit length, psi/in. (N/m3)As regenerator matrix surface area, in.
2 (m2)
c Cp=Cv specific heat ratio, noneq fluid local density, lb s2/ft4 (N s2/m4)
b porosity, none
l viscosity, lb s/ft2 (N s2/m2)
DQ refrigeration loss per cycle, BTU (J)
Re the flow Reynolds number, none
Pe Peclet number, none
Pr Prandtl number, none
Q ideal refrigeration per cycle, BTU (J)
Rpf regenerator performance factor, W/C psi/in.(W m3/N)
T2 temperature, R (K)
T3 temperature, R (K)
u fluid velocity, ft/s (m/s)
V3 volume, in.3 (m3)
V4 volume, in.3 (m3)
Fig. 2. Screen laminate element.
Fig. 1. Single screen mesh stacked regenerator made of 650 screen
disks.
Fig. 3. Laminate screen block.
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DQ
Qideal
1 e
c 1
T2=T3 1
lnV4=V3
1
For example:
e 0:99 regenerator effectivenessc 1:67 specific heat ratio Cp=CvT2 540 R (300 K) rejection temperatureT3 140 R (77.7 K) cold end temperatureV4=V3 1:24 expansion ratioe regenerator effectiveness
T2 rejection temperature
T3 cold end temperature
V3 volume of expansion space at beginning of
expansion process
V4 volume of expansion space at end of expansion
process
A cryo-cooler with 1.24 expansion ratio operating
between 540 R (300 K) rejection temperature and140 R (77.7 K) cold end temperature, using Helium as a
working fluid will lose 20% of its refrigeration power if
the regenerator effectiveness is 99% instead of 100%.
This example emphasizes the critical role of the regen-
erator in Stirling cycle refrigerators performance and
efficiency.
4. Single screen disk regenerator matrix
The current regenerator design and assembly meth-
ods make it extremely difficult and costly to manufac-ture regenerators in production environment that meet
high effectiveness requirements consistently and in rea-
sonable yield. Regenerator effectiveness is depended on
and extremely sensitive to variations in surface area,
void volume (also known as dead volume), flow rate,
stacking pressure, mesh placement/orientation, screen
contamination and more. These variables are affected by
workmanship, process control and manufacturing tol-
erances. Also, it is extremely difficult to fabricate screen
elements of thin wire due to required die tolerances.
Most of these manufacturing problems (discussed
below) are due to the fact that the current regenerator
matrix element (Fig. 4) is very small, light and can beeasily bent or damaged during the fill process. The
regenerator tube fill process requires the technician to
handle 850 elements or more per tube, making the task
time consuming, difficult to control and inconsistent.
Stacking errors are practically unavoidable resulting in
low manufacturing yield and low performance.
Surface area of a filled regenerator is proportional to
the number of screen elements in the regenerator tube.
The number of screens in the tube can vary greatly due
to the wire diameter of the screen and the technicians
ability to maintain the required stacking pressure.
Void volume can vary greatly among regenerators due
to wire size tolerances, stacking pressure, screen element
size, screen disk flatness, regenerator tube internal
diameter manufacturing tolerances and the presence of
folded or bent screens.
Flow rate varies due to stacking pressure variations
caused by regenerator fill error, screen to screen weave
alignment and all the variables controlling surface areaand void volume mentioned previously.
Thermal contact resistance value depends on stacking
pressure, total number of screens in the tube, screen to
screen orientation and screen wire surface finish. Any
variation in the above stacking parameter will result in
refrigeration loses.
4.1. Analysisregenerator performance
In general the regenerator performance is directly
proportional to the matrix surface area and convection
coefficient and inversely proportional to pressure dropper unit length of the regenerator matrix. The relation-
ship between these three matrix design parameters is the
Regenerator Performance Factor and defined as follows:
Rpf Ash
op=ox2
where Rpf regenerator performance factor, W/(C psi/in.); As regenerator matrix surface area, in.
2; hmatrix convection coefficient, W/in.2 C; oP=oXpressure drop per matrix unit length, psi/in.
The matrix Rpf value is calculated at a given volu-
metric flow rate and it is the ratio between the energyflow per C, DT and the matrix local pressure gradient.
The goal is to maximize this value by increasing surface
area, convection coefficient and minimizing pressure
gradient.
As, regenerator matrix surface area calculations: sur-
face area of a given matrix is simply the total effective
area of the screen wires making direct contact with the
fluid. This value can be calculated or obtained from the
manufacturer. The area is dependent on wire size, weave
type, mesh density (wire weaved per in.) and total
number of screen elements in the matrix.
Fig. 4. Single screen elements.
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oP=oX, pressure gradient calculations: the calculationof pressure drop in porous media is given by the fol-
lowing equation [2,3]:
op
ox
f
dh
qu2
23
where f friction factor; q fluid local density;dk hydraulic diameter; u fluid velocity.
dh hydraulic diameter and friction factor calcula-tions: the hydraulic diameter is the matrix wire diameter
modified by the porosity and it allows us to determine
the local Reynolds number of the flow by simulating it
as a simplified case of flow across a cylindrical body.
The end result is that the drag produced by flow in
porous media of certain wire diameter is equivalent to
drag produced by free flow over a cylinder with diameter
dk.
The hydraulic diameter equation is [2]:
dh b
1 b dw 4
where b porosity, porosity defined as: void volume/total matrix volume; Re the flow Reynolds numberequation is [2]:
Re qudh=l 5
where dk hydraulic diameter, calculated using Eq. (4);l viscosity; f friction.
Darcy-type friction factor calculation: the equation
for calculating the friction factor is based on Ergun
equation (Table 2) which was modified to better track
observed test data.
The equation is [2]:
f 129=Re 2:91Re0:103 6
where Reynolds number is determined by Eq. (5).
We are now ready to calculate the pressure drop
using Eq. (3) by substituting the values of f, friction
factor and dk, hydraulic diameter.
To calculate the regenerator performance factor Rpf,
we will have to determine the convection coefficient h.
h convection coefficient. The convection coefficienth, is a function of Nusselt number, the fluid conductivity
k and the hydraulic diameter dk. It can be calculated
using the following equation [2]:
h Nuk
dh7
Nusselt number is a function of Peclet number Nu and
the porosity b and calculated using the following equa-
tions [2]:
Nu 1 0:99Pe0:66b1:79 8
where b porosity; PePeclet number.Peclet number can be calculated using the Reynolds
number which has been determined previously and
Prandtl which can be calculated using the following
equations:
Pe RePr
Prandtl number is a function of fluid viscosity l, thermal
conductivity k and specific heat Cp of the working fluid
and can be calculated using the following equation:
PrPrandtl number
Pr lCp=k 9
We are now able to calculate the convection coefficient
and the regenerator performance factor using Eqs. (3)
and (7) and the total surface area As.
5. Test program
Using the above analysis model we calculated the
Regenerator Performance Factor for a variety of lami-
nate and single screen filled regenerators which wereconstructed from different types of mesh. Two regener-
ators were filled with single screen disk elements 400
mesh 0.0012 twill weave (FLIR Systems standard pro-
duction regenerator matrix) and the second one was
filled with a 400 mesh 0.0009 wire diameter plain weave.
Both regenerators were filled according to FLIRs man-
ufacturing methods and processes.
Three additional regenerators were filled with differ-
ent laminates.
The first regenerator was filled with 400 mesh 0.0012
twill weave laminate to 2/3 of the standard length in
order to maintain adequate flow rate. The second
regenerator was filled to the entire length with a 325
mesh 0.0014 wire laminate.
And the third one was filled to the entire length with a
mix of different laminates made from 400, 200, and 325
mesh in order to maximize Rpf number. Additional
laminates were tested and are identified in Table 1.
The Rpf number was calculated at room temperature
using Helium as a working fluid and at a flow velocity of
2.58 ft/s. The analysis results of few mesh types are
summarized at the Table 1. Few regenerators were built
(Table 2) and integrated into the same integrated cooler
Dewar assembly (IDCA) (Table 3). The cooling power
was measured at 77 at 300 K ambient (Fig. 5) using aDewar with active heat load and a temperature diode
mounted on the cold tip of the Dewar. The test results
are summarized in the Table 2.
6. Summary
A new type of regenerator matrix (Fig. 6) has recently
been developed at FLIR SystemsBoston. The alter-
nate design is essentially a woven screen laminate fab-
ricated by bonding screen sheets using a sintering
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process. Three laminate and two screen disk regenera-
tors were analyzed, built and tested. The cooling power
was measured, summarized in Table 2 and plotted as a
function of the Regenerator Performance Factor Rpf.
The performance plot clearly demonstrates that the
correlation between the calculated Performance Factor
and Cooling Power is strong and linear. In general,
regenerators with high Rpf always performed better. We
Table 1
Regenerator matrix details summary
dk, in. (m) b dw, in. (m) op=ox, psi/in.(N/m3)
h, W/in.2/C
(W/m2/K)
As, in2 (m2) Rpf, regenerator
performance
factor, W in./Cpsi
(W m3/KN)
Laminate 400
mesh 0.0012 twill
0.0014
(3.56E)
05)
0.54 0.0012
(3.05E)
05)
3.30
(3.73E)
01)
3.12
(2.01E)
03)
27.0
(1.74E)
02)
25.4 (9.4E)05)
Laminate 325
mesh 0.0014 twill
0.00177
(4.5E)05)
0.56 0.0014
(3.56E)05)
2.15
(2.43E)01)
2.92
(1.88E)03)
32.3
(2.08E)02)
43.9 (1.62-04)
Laminate 200
mesh 0.0021 twill
0.003
(7.62E)05)
0.59 0.0021
(5.33E)05)
0.782
(8.83E)02)
2.45 (1.58-03) 21.2
(1.37E)02)
66.6* (2.45E)04)
Mixed laminates (4)
400 mesh 0.0012
n/a n/a n/a 1.75
(8.83E)02)
Length
weighted
average
2.82
(1.82E)03)
Surface area
weighted
average
28.9
(1.86E)02)
Total surface
area
46.5 (3.84E)04)
(26) 325 mesh 0.0014
(17) 200 mesh 0.0021
Laminate 280
mesh 0.0013 plain
0.0018
(4.52E)05)
0.583 0.0013
(3.30E)05)
2.04
(2.30E)01)
3.11
(2.01E)03)
34.75
(2.24E)02)
53.0* (1.95E)04)
Laminate 325
mesh 0.0011 plain
0.00158
(4.01E)05)
0.59 0.0011
(2.79E)05)
2.66
(3.01E)01)
3.42
(2.21E)03)
40.59
(2.62E)02)
52.3 (1.92E)04)
Laminate 250
mesh 0.0014 plain
0.0021
(3.05E)
05)
0.598 0.0014
(3.56E)
05)
1.58
(1.79E)
01)
3.03
(1.95E)
03)
31.45
(2.03E)
02)
60.5* (2.22E)04)
Laminate 230
mesh 0.0014 plain
0.00236
(5.99E)05)
0.63 0.0014
(3.56E)05)
1.24
(1.40E)01)
3.1 (2.00E)03) 29.72
(1.92E)02)
74.4* (2.74E)04)
Single screen element
400 mesh 0.0012 twill
0.0017
(4.32E)05)
0.59 0.0012
(3.05E)05)
2.25
(2.54E)01)
3.27
(2.11E)03)
35.83
(2.31E)02)
52.1 (1.92E)04)
Single screen element
400 mesh 0.0009 plain
0.0015
(3.81E)05)
0.63 0.0009
(2.29E)05)
2.83 (3.2E)01) 3.92
(2.53E)02)
44.24
(2.85E)02)
61.4 (2.26E)04)
Table 2
Cooling power test results summary
Rege ne rator type de script ion Rege ne rator performance c oe . W in./K/psi (W m3/KN) Cooling power test (mW)
400 Mesh twill 0.0012, (31) laminates 25.4 (9.4E)05) 350
325 Mesh twill 0.0014, (48) laminates 43.9 (1.62E)
05) 386Mesh twilla 0.0012, (650) single screen disks 52.07 (1.92E)04) 420
400 Mesh plain 0.0009, (850) single screen disks 61.36 (2.26E)04) 466
Mixed laminate matrix regen 46.45 (3.84E)04) 400
(4) 400 Mesh 0.0012 wire dia. twill laminate
(26) 325 Mesh 0.0014 wire dia. twill laminate
(17) 200 Mesh 0.0021 wire dia. twill laminate
325 Mesh plain weave (49) laminate sand blasted 52.3 (1.92E)04) 430
325 Mesh four layer laminate 64.8 (2.38E)04) 469
325 And 400 mesh mixed 66 and 150 4 layer laminates 64.6 (2.37E)04) 478a Baseline design.
Table 3
Cost analysisscreen disk vs. laminate matrixItem Unit material
cost
Units required Material cost
total
Labor hours Hourly rate Labor cost total Total regenerator cost
Laminate $1.00 50 $50.0 0.3 $35 $10.5 $60.5
Screen disk 0.070 850.0 $59.5 3.0 $35 $105.0 $164.5
Delta )$9.5 )$94.5 )$104.5
Total savings: $104.5 per unit ($209,000 per year at current production rate).
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managed to reduce conductive losses by increasing the
laminate surface roughness.
The cooling power of the standard matrix regenerator
currently in production is in the range of 380440 mW
with an average 410 mW, while the laminate design
regenerator was able to produce 400478 mW with an
average 440 mW of refrigeration depending on thelaminate type (Table 2). The measured cooling power
shows that the laminate regenerator performance is
similar or better than the average single screen disk
regenerator and cost 63% less to manufacture.
We plan to further optimize the design by using dif-
ferent mesh laminates in a regenerator to match the
temperature gradient along it. This allows us to take
advantage of the change in viscosity ofHe as a function
of temperature. Also, we plan to test laminate fabricated
in a variety of orientations.
7. Conclusions
So far, the performance of the new laminate regener-
ator is equal or better than the average standard sin-
gle screen filled matrix regenerator currently in
production.
The correlation between the calculated Rpf and cool-
ing power is good.
The potential for higher performance laminate is sig-
nificant.
The reduction in the number of matrix elements per
regenerator provides more than 63% reduction in
cost.
The ability to design a regenerator with mixed lami-
nates provides an additional system optimization
method.
Fabrication of ultra fine mesh disks will not be prac-
tical with out the use of laminates.
References
[1] Flynn TM. Cryogenic engineering. New York: Marcel Dekker, Inc.;
1997. p. 327.[2] Gedeon D. Baseline Stirling modeling. Athens, OH: Gedeon
Associates; 1999.
[3] Macdonald IF, El-Sayed MS, Mow K, Dullien FAL. Flow through
porous media-Ergun equation revisited. Ind Eng Chem Fundam
1979;(18):199208.
Fig. 5. IDCA cooling power vs. regenerator performance factor.
Fig. 6. Screen laminate regenerator.
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