U.S. patent application number 10/245869 was filed with the patent office on 2003-04-17 for modular pressure swing adsorption apparatus.
Invention is credited to Doman, David G., Keefer, Bowie Gordon, McLean, Christopher R..
Application Number | 20030070550 10/245869 |
Document ID | / |
Family ID | 22073847 |
Filed Date | 2003-04-17 |
United States Patent
Application |
20030070550 |
Kind Code |
A1 |
Keefer, Bowie Gordon ; et
al. |
April 17, 2003 |
Modular pressure swing adsorption apparatus
Abstract
A rotary module for implementing a high frequency pressure swing
adsorption process comprises a stator and a rotor rotatably coupled
to the stator. The stator includes a first stator valve surface, a
second stator valve surface, a plurality of first function
compartments opening into the first stator valve surface, and a
plurality of second function compartments opening into the second
stator valve surface. The rotor includes a first rotor valve
surface in communication with the first stator valve surface, a
second rotor valve surface in communication with the second stator
valve surface, and a plurality of flow paths for receiving
adsorbent material therein. Each flow path includes a pair of
opposite ends, and a plurality of apertures provided in the rotor
valve surfaces and in communication with the flow path ends and the
function ports for cyclically exposing each said flow path to a
plurality of discrete pressure levels between the upper and lower
pressures for maintaining uniform gas flow through the first and
second function compartments.
Inventors: |
Keefer, Bowie Gordon;
(Vancouver, CA) ; Doman, David G.; (Delta, CA)
; McLean, Christopher R.; (Vancouver, CA) |
Correspondence
Address: |
KLARQUIST SPARKMAN, LLP
121 SW SALMON STREET
SUITE 1600
PORTLAND
OR
97204
US
|
Family ID: |
22073847 |
Appl. No.: |
10/245869 |
Filed: |
September 16, 2002 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10245869 |
Sep 16, 2002 |
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09584269 |
Sep 18, 2000 |
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6451095 |
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09584269 |
Sep 18, 2000 |
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PCT/CA98/01103 |
Dec 1, 1998 |
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60067120 |
Dec 1, 1997 |
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Current U.S.
Class: |
96/125 |
Current CPC
Class: |
B01D 53/0454 20130101;
B01D 2256/16 20130101; B01D 2257/102 20130101; B01D 53/06 20130101;
B01D 53/0431 20130101; B01D 53/047 20130101; B01D 2259/40005
20130101; B01D 53/0476 20130101; B01D 2253/108 20130101 |
Class at
Publication: |
96/125 |
International
Class: |
B01D 053/06 |
Claims
We claim:
1. A rotary module for implementing a pressure swing adsorption
process having an operating pressure cycling between an upper
pressure and a lower pressure for extracting a first gas fraction
and a second gas fraction from a gas mixture including the first
and second fractions, the rotary module comprising: a stator
including a first stator valve surface, a second stator valve
surface, a plurality of first function compartments opening into
the first stator valve surface, and a plurality of second function
compartments opening into the second stator valve surface; and a
rotor rotatably coupled to the stator and including a first rotor
valve surface in communication with the first stator valve surface,
a second rotor valve surface in communication with the second
stator valve surface, a plurality of flow paths for receiving
adsorbent material therein, each said flow path including a pair of
opposite ends, and a plurality of apertures provided in the rotor
valve surfaces and in communication with the flow path ends and the
function ports for cyclically exposing each said flow path to a
plurality of discrete pressure levels between the upper and lower
pressures for maintaining uniform gas flow through the first and
second function compartments.
2. The rotary module according to claim 1, wherein the function
compartments are shaped to provide uniform gas flow through the
flow paths.
3. The rotary module according to claim 1, wherein at least one of
the valve surfaces includes a sealing strip for reducing gas flow
loss between the valve surfaces, the sealing strip including a
tapered portion for providing uniform gas flow through the flow
paths.
4. The rotary module according to claim 3, wherein the sealing
strip is shaped to provide rapid closing of the flow paths.
5. The rotary module according to claim 1, wherein each said
function compartment simultaneously communicates with at least two
flow paths for providing uniform gas flow through the function
compartments.
6. The rotary module according to claim 1, wherein each said
function compartment is coupled immediately adjacent to a
respective end of a respective one of the flow paths for
implementing high frequency pressure swing adsorption.
7. The rotary module according to claim 6, wherein the function
compartments are positioned a distance from the respective flow
path ends sufficient for implementing the pressure swing adsorption
process at a rotor rotational speed of at least 20 revolutions per
minute.
8. The rotary module according to claim 1, wherein the function
compartments include a plurality of pressurization compartments for
subjecting the flow paths to a plurality of incremental pressures
increases.
9. The rotary module according to claim 8, wherein the
pressurization compartments comprise gas feed compartments opening
into the first stator valve surface for delivering the gas mixture
to the flow paths at a plurality of incrementally different
pressures.
10. The rotary module according to claim 8, wherein the
pressurization compartments comprise light reflux return
compartments opening into the second stator valve surface for
delivering light reflux gas to the flow paths at a plurality of
incrementally different pressures.
11. The rotary module according to claim 1, wherein the first
function compartments include a plurality of blowdown compartments
for subjecting the flow paths to a plurality of incremental
pressure drops.
12. The rotary module according to claim 11, wherein the blowdown
compartments comprise light reflux exit compartments opening into
the second stator valve surface for removing light reflux gas from
the flow paths at a plurality of incrementally different
pressures.
13. The rotary module according to claim 11, wherein the blowdown
compartments comprise countercurrent blowdown compartments opening
into the first stator valve surface for removing heavy product gas
from the flow paths at a plurality of incrementally different
pressures.
14. The rotary module according to claim 1, wherein the second
function compartments include a plurality of cocurrent blowdown
compartments for subjecting the flow paths to a plurality of
incremental pressure drops, and a plurality of light reflux return
compartments communicating with the cocurrent blowdown compartments
for subjecting the flow paths to a plurality of incremental
pressure increases, and the stator includes pressure let-down means
coupled between the cocurrent blowdown compartments and the light
reflux return compartments for delivering gas removed from the
cocurrent blowdown compartments at reduced pressure to the light
reflux return compartments.
15. The rotary module according to claim 14, wherein the pressure
let-down means comprises one of mechanical expansion stages,
restrictor orifices and throttle valves.
16. The rotary module according to claim 14, wherein the second
function compartments include a light product compartment, and the
pressure let-down means comprises an expander coupled to the
cocurrent blowdown compartments and the light reflux return
compartments, and a compressor coupled to the light product
compartment and to the expander for boosting light product gas
pressure.
17. The rotary module according to claim 1, wherein the first
function compartments include a plurality of countercurrent
blowdown compartments for subjecting the flow paths to a plurality
of incremental pressure drops, and a heavy reflux return
compartment communicating with at least one of the countercurrent
blowdown compartments, and the stator includes a reflux compressor
coupled between the countercurrent blowdown compartments and the
heavy reflux return compartment for delivering gas removed from the
countercurrent blowdown compartments at increased pressure to the
heavy reflux return compartments.
18. The rotary module according to claim 1, wherein the function
compartments are disposed around the respective valve surfaces for
conveying gas along the flow paths in a common predetermined
sequence for each flow path, the sequence for each flow path
comprising delivering the gas mixture at the upper pressure from a
gas feed function compartment to the flow path end adjacent the
first rotor valve surface while removing light product gas at the
upper pressure from the flow path end adjacent the second rotor
valve surface to a light product function compartment, removing
heavy product gas at the lower pressure from the flow path end
adjacent the first rotor valve surface to a heavy product gas
function compartment, and delivering gas at a pressure intermediate
the upper and lower pressure from a repressurization function
compartment to the flow path end adjacent the first rotor valve
surface ahead of the gas feed function compartment.
19. The rotary module according to claim 1, wherein the function
compartments are disposed around the respective valve surfaces for
conveying gas along the flow paths in a common predetermined
sequence for each flow path, the sequence for each flow path
comprising delivering the gas mixture at the upper pressure from a
gas feed function compartment to the flow path end adjacent the
first rotor valve surface while removing light product gas at the
upper pressure from the flow path end adjacent the second rotor
valve surface to a light product function compartment, removing gas
at a pressure intermediate the upper and lower pressures from the
flow path end adjacent the second rotor valve surface to a
cocurrent blowdown function compartment, and removing heavy product
gas at the lower pressure from the flow path end adjacent the first
rotor valve surface to a heavy product gas function
compartment.
20. The rotary module according to claim 1, wherein the function
compartments are disposed around the respective valve surfaces for
conveying gas along the flow paths in a common predetermined
sequence for each flow path, the sequence for each flow path
comprising delivering the gas mixture at the upper pressure from a
gas feed function compartment to the flow path end adjacent the
first rotor valve surface while removing light product gas at the
upper pressure from the flow path end adjacent the second rotor
valve surface to a light product function compartment, removing gas
at a pressure intermediate the upper and lower pressures from the
flow path end adjacent the first rotor valve surface to a
countercurrent blowdown function compartment, and removing heavy
product gas at the lower pressure from the flow path end adjacent
the first rotor valve surface to a heavy product gas function
compartment.
21. The rotary module according to claim 1, wherein each said flow
path includes a laminated sheet adsorber.
22. A rotor module for use with a stator for implementing a
pressure swing adsorption process having an operating pressure
cycling between an upper pressure and a lower pressure, the rotor
module comprising: an annular rotor including a first rotor valve
surface for communicating with a first stator valve surface of the
stator, a second rotor valve surface for communicating with a
second stator valve surface of the stator, a plurality of flow
paths spaced around the rotor and extending between the rotor valve
surfaces, and a plurality of apertures provided in the rotor valve
surfaces in communication with the flow paths for cyclically
exposing each said flow path to a plurality of discrete pressure
levels between the upper and lower pressures; and a plurality of
adsorbent beds disposed in the flow paths in communication with the
apertures.
23. The rotor module according to claim 22, wherein each said
adsorbent bed comprising at least two laminated adsorbent sheets,
each said sheet including a reinforcement matrix, an adsorbent
material deposited therein, a binder for securing the adsorbent
material to the binder, and a spacer provided between the two
laminated sheets for providing a flow channel therebetween.
24. The rotor module according to claim 23, wherein the
reinforcement material is selected from glass fiber, metal wire
matrix, metal foil, inorganic fiber and organic fiber.
25. The rotor module according to claim 23, wherein the adsorbent
material comprises zeolite crystallites.
26. The rotor module according to claim 22, wherein the rotor has
an inner circumference and an outer circumference, and the
adsorbent beds have a width, the width being greater adjacent the
outer circumference than adjacent the inner circumference and
increasing in magnitude with distance from the inner
circumference.
27. The rotor module according to claim 22, wherein the adsorbent
beds have a curved shape.
28. The rotor module according to claim 22, wherein the adsorbent
beds comprise a plurality of adsorbent pellets, each said pellet
comprising an inert core coated with an adsorbent material.
29. The rotor module according to claim 28, wherein the inert core
is selected from iron group metals and oxides thereof.
30. The rotor module according to claim 28, wherein the pellet has
a volume, and the inert core comprises half of the volume.
31. The rotor module according to claim 22, wherein the flow paths
include a pair of opposite ends, and each said aperture is disposed
immediately adjacent to a respective one of the opposite ends.
32. A pressure swing adsorption system for extracting a first gas
fraction and a second gas fraction from a gas mixture including the
first and second fractions, the pressure swing adsorption system
comprising: a rotary module coupled to a gas feed manifold, a heavy
product manifold, and a light product manifold, the rotary module
comprising: stator including a first stator valve surface, a second
stator valve surface, a plurality of first function compartments
opening into the first stator valve surface, and a plurality of
second function compartments opening into the second stator valve
surface; and a rotor rotatably coupled to the stator and including
a first rotor valve surface in communication with the first stator
valve surface, a second rotor valve surface in communication with
the second stator valve surface, a plurality of flow paths for
receiving adsorbent material therein, each said flow path including
a pair of opposite ends, and a plurality of apertures provided in
the rotor valve surfaces and in communication with the flow path
ends and the function ports; and compression/expansion machinery
coupled to the rotary module for maintaining the function ports at
a plurality of discrete pressure levels between an upper pressure
and a lower pressure for maintaining uniform gas flow through the
first and second function compartments.
33. The pressure swing adsorption system according to claim 32,
wherein the function compartments include a plurality of gas feed
compartments, and the compression/expansion machinery comprises a
multi-stage compressor including a plurality of pressure output
ports, each said pressure output port being coupled to a respective
one of the feed compartments for delivering feed gas to the flow
paths at a plurality of pressure increments.
34. The pressure swing adsorption system according to claim 33,
wherein the multi-stage compressor comprises a centrifugal
compressor having a plurality of stages, each said stage including
a gas inlet, a diffuser, and an impeller coupled to the gas inlet
and having an axis of rotation for accelerating gas from the gas
inlet towards the diffuser.
35. The pressure swing adsorption system according to claim 33,
wherein the multi-stage compressor comprises a multi-stage axial
flow split stream compressor including a plurality of annular
stator rings of progressively decreasing diameter, each said stator
ring including an annular flow area and a plurality of stator
blades, and a rotor having an axis of rotation and including a
plurality of rotor blades cooperating with the stator blades for
compressing gas flow through the flow area, at least one of the
said stator rings further including a collector and a diffuser for
apportioning the compressed gas flow between the collector and the
flow area of a subsequent one of the stator rings.
36. The pressure swing adsorption system according to claim 33,
wherein the function compartments include a plurality of blowdown
compartments, and the compression/expansion machinery includes a
multi-stage vacuum pump coupled to the compressor, the vacuum pump
including a plurality of pressure inlet ports, each said pressure
inlet port being coupled to a respective one of the blowdown
compartments for receiving blowdown gas from the flow paths at a
plurality of pressure increments.
37. The pressure swing adsorption system according to claim 33,
wherein the function compartments include a plurality of blowdown
compartments, and the pressure swing adsorption system includes a
plurality of throttle orifices coupled to the blowdown compartments
for releasing blowdown gas from the flow paths at a plurality of
pressure increments.
38. The pressure swing adsorption system according to claim 32,
wherein the function compartments include a plurality of
countercurrent blowdown compartments and a plurality of cocurrent
blowdown compartments, and the compression/expansion machinery
comprises a first expander coupled to the countercurrent blowdown
compartments and a second expander coupled to the first expander
and to the cocurrent blowdown compartments.
39. The pressure swing adsorption system according to claim 36,
wherein the function compartments include a plurality of gas feed
compartments, and the compression/expansion machinery includes a
compressor coupled to the gas feed compartments and to the first
and second expanders.
40. The pressure swing adsorption system according to claim 33,
wherein the multi-stage turbine is coupled to a plurality of said
rotary modules, and the gas feed manifold, the heavy product
manifold, and the light product manifold are coupled to the
plurality of rotary modules.
41. A multi-stage axial flow split stream compressor comprising: a
plurality of annular stator rings of progressively decreasing
diameter, each said stator ring including an annular flow area and
a plurality of stator blades; and a rotor having an axis of
rotation and including a plurality of rotor blades cooperating with
the stator blades for compressing gas flow through the flow area,
at least one of the stator rings further including a collector and
a diffuser for apportioning the accelerated gas flow between the
collector and the flow area of a subsequent one of the stator
rings.
Description
FIELD OF THE INVENTION
[0001] The present invention relates to an apparatus for separating
gas fractions from a gas mixture having multiple gas fractions. In
particular, the present invention relates to a rotary valve gas
separation system having a plurality of rotating adsorbent beds
disposed therein for implementing a pressure swing adsorption
process for separating out the gas fractions.
BACKGROUND OF THE INVENTION
[0002] Pressure swing adsorption (PSA) and vacuum pressure swing
adsorption (VPSA) separate gas fractions from a gas mixture by
coordinating pressure cycling and flow reversals over an adsorbent
bed which preferentially adsorbs a more readily adsorbed component
relative to a less readily adsorbed component of the mixture. The
total pressure of the gas mixture in the adsorbent bed is elevated
while the gas mixture is flowing through the adsorbent bed from a
first end to a second end thereof, and is reduced while the gas
mixture is flowing through the adsorbent from the second end back
to the first end. As the PSA or VPSA cycle is repeated, the less
readily adsorbed component is concentrated adjacent the second end
of the adsorbent bed, while the more readily adsorbed component is
concentrated adjacent the first end of the adsorbent bed. As a
result, a "light" product (a gas fraction depleted in the more
readily adsorbed component and enriched in the less readily
adsorbed component) is delivered from the second end of the bed,
and a "heavy" product (a gas fraction enriched in the more strongly
adsorbed component) is exhausted from the first end of the bed.
[0003] The conventional system for implementing pressure swing
adsorption or vacuum pressure swing adsorption uses two or more
stationary adsorbent beds in parallel, with directional valving at
each end of each adsorbent bed to connect the beds in alternating
sequence to pressure sources and sinks. However, this system is
often difficult and expensive to implement due to the complexity of
the valving required.
[0004] Furthermore, the conventional PSA or VPSA system makes
inefficient use of applied energy, because feed gas pressurization
is provided by a compressor whose delivery pressure is the highest
pressure of the cycle. In PSA, energy expended in compressing the
feed gas used for pressurization is then dissipated in throttling
over valves over the instantaneous pressure difference between the
adsorber and the high pressure supply. Similarly, in VPSA, where
the lower pressure of the cycle is established by a vacuum pump
exhausting gas at that pressure, energy is dissipated in throttling
over valves during countercurrent blowdown of adsorbers whose
pressure is being reduced. A further energy dissipation in both
systems occurs in throttling of light reflux gas used for purge,
equalization, cocurrent blowdown and product pressurization or
backfill steps.
[0005] Numerous attempts have been made at overcoming the
deficiencies associated with the conventional PSA or VPSA system.
For example, Siggelin (U.S. Pat. No. 3,176,446), Mattia (U.S. Pat.
No. 4,452,612), Davidson and Lywood (U.S. Pat. No. 4,758,253),
Boudet et al (U.S. Pat. No. 5,133,784), Petit et al (U.S. Pat. No.
5,441,559) and Schartz (PCT publication WO 94/04249) disclose PSA
devices using rotary distributor valves having rotors fitted with
multiple angularly separated adsorbent beds. Ports communicating
with the rotor-mounted adsorbent beds sweep past fixed ports for
feed admission, product delivery and pressure equalization.
However, these prior art rotary distributor valves are
impracticable for large PSA/VPSA units, owing to the weight of the
rotating assembly. Furthermore, since the valve faces are remote
from the ends of the adsorbent beds, these rotary distributor
valves have considerable dead volume for flow distribution and
collection. As a result, the prior art rotary distributor valves
have poor flow distribution, particularly at high cycle
frequencies.
[0006] Hay (U.S. Pat. No. 5,246,676) and Engler (U.S. Pat. No.
5,393,326) provide examples of vacuum pressure swing adsorption
systems which reduce throttling losses in an attempt to improve the
efficiency of the gas separation process system. The systems taught
by Hay and Engler use a plurality of vacuum pumps to pump down the
pressure of each adsorbent bed sequentially in turn, with the pumps
operating at successively lower pressures, so that each vacuum pump
reduces the pressure in each bed a predetermined amount. However,
with these systems, the vacuum pumps are subjected to large
pressure variations, stressing the compression machinery and
causing large fluctuations in overall power demand. Because
centrifugal or axial compression machinery cannot operate under
such unsteady conditions, rotary lobe machines are typically used
in such systems. However, such machines have lower efficiency than
modem centrifugal compressors/vacuum pumps working under steady
conditions.
[0007] Accordingly, there remains a need for a PSA/VPSA system
which is suitable for high volume and high frequency production,
while reducing the losses associated with the prior art
devices.
SUMMARY OF THE INVENTION
[0008] It is an object of the present invention provide a rotary
module for implementing a high frequency pressure swing adsorption
process with high energy efficiency.
[0009] The rotary module, in accordance with the invention,
comprises a stator and a rotor rotatably coupled to the stator. The
stator includes a first stator valve surface, a second stator valve
surface, a plurality of first function compartments opening into
the first stator valve surface, and a plurality of second function
compartments opening into the second stator valve surface. The
rotor includes a first rotor valve surface in communication with
the first stator valve surface, a second rotor valve surface in
communication with the second stator valve surface, and a plurality
of flow paths for receiving adsorbent material therein. Each said
flow path includes a pair of opposite ends, and a plurality of
apertures provided in the rotor valve surfaces and in communication
with the flow path ends and the function ports for cyclically
exposing each said flow path to a plurality of discrete pressure
levels between the upper and lower pressures for maintaining
uniform gas flow through the first and second function
compartments.
[0010] During pressurization and blowdown steps, the several
adsorbers passing through the step will converge to the nominal
pressure level of each step by a throttling pressure equalization
from the pressure level of the previous step experienced by the
adsorbers. Flow is provided to the adsorbers in a pressurization
step or withdrawn in a blowdown step by compression machinery at
the nominal pressure level of that step. Hence flow and pressure
pulsations seen by the compression machinery at each intermediate
pressure level are minimal by averaging from the several adsorbers
passing through the step, although each adsorber undergoes large
cyclic changes of pressure and flow.
[0011] During the pressurization steps for each adsorber, either
(or both) of the apertures of an adsorber already at a pressure is
(are) opened respectively to a first or second pressurization
compartment at a stepwise higher pressure. Similarly, during the
pressurization steps for each adsorber, either (or both) of the
apertures of an adsorber already at a pressure is (are) opened
respectively to a first or second pressurization compartment at a
stepwise lower pressure. Equalization then takes place by flow
through the open aperture(s) from the pressurization/blowdown
compartment into the adsorber, which by the end of the
pressurization/blowdown step has attained approximately the same
pressure as the pressurization/blowdown compartment(s). Each
pressurization/blowdown compartment is in communication with
typically several adsorbers being pressurized (in differing angular
and time phase) at any given time, so the pressure in that
compartment and the pressurization flow to that compartment are
substantially steady.
[0012] The flow path through the adsorbers may be radial or axial.
If the adsorbers are configured for radial flow, the first valve
surface would preferably be radially inward when the less strongly
adsorbed gas fraction has much higher density that the more
strongly adsorbed fraction, and the first valve surface would
preferably be radially outward when the less strongly adsorbed gas
fraction has much lower density than the more strongly adsorbed
fraction. Hence, for hydrogen purification in a radial flow
embodiment, the feed gas would preferably be admitted to (and the
higher molecular weight impurity fraction as heavy product is
exhausted from) the first valve surface at an outer radius, while
the hydrogen as first product gas is delivered from the second
valve surface.
[0013] The present invention also includes the alternatives of (1)
layered or laminated thin sheet adsorbers and (2) the centrifugally
stabilized fine particle granular adsorbers to enable operation at
exceptionally high cycle frequency. PSA cycle frequencies to at
least 100 cycles per minute are practicable within the present
invention, and will enable process intensification so that high
productivity can be realized from compact modules. Cycle
frequencies more rapid than about 50 cycles per minute will be
achieved preferably with the layered thin sheet adsorbers, with the
flow path in flow channels tangential to and between adjacent pairs
of adsorbent loaded sheets, to obtain lower frictional pressure
drop at high frequency than granular adsorbent.
[0014] Preferably, the increments between adjacent pressure levels
are sized so that the gas flows entering or exiting the module are
substantially steady in both flow velocity and pressure. As a
result, the module can be operated with centrifugal or axial flow
compressors and expanders, for most favourable efficiency and
capital cost economies of scale. To reduce throttling losses, it is
also preferred that the function compartments are shaped to provide
uniform gas flow through the flow paths and/or the valve surfaces
include sealing strips having tapered portions for providing
uniform gas flow through the flow paths.
[0015] Since the orifices providing the valving function are
immediately adjacent to the ends of the flow paths, the dead volume
associated with prior art distribution manifolds is substantially
reduced. Also, since the compartments communicating with the first
and second valve surfaces are external to the valving function, the
compartments do not contribute to dead volume of the adsorbers. As
a result, high frequency pressure/vacuum swing adsorption is
possible.
[0016] Also, in contrast to prior art PSA devices whose pressure
vessels are subject to pressure cycling and consequent fatigue
loading, the pressure vessel of the present invention operates
under substantially static stresses, because each of the
compartments operates under steady pressure conditions. Mechanical
stresses on the rotor and its bearings are relatively small,
because only small frictional pressure drops (at most equal to the
interval between adjacent intermediate pressures) apply in the flow
direction, while transverse pressure gradients between the adsorber
elements are also small owing to the large number of elements.
These features are important, since pressure vessel fatigue is a
major concern and limitation in the design of PSA systems,
especially working with corrosive gases or hydrogen at higher
pressure or higher cycle frequency.
[0017] Further, by providing multiple closely spaced intermediate
pressure levels, with substantially constant flow and pressure at
each level, the present invention facilitates energy efficient
application of multistage feed compressors and vacuum pumps
(including centrifugal or axial compression machines) for feed
compression, heavy product exhaust and heavy reflux compression; as
well as multistage expanders (including radial inflow turbines,
axial turbines and partial admission impulse turbines). Positive
displacement (reciprocating piston, rotary piston, or progressive
cavity such as screw or scroll machines) compression and expansion
machinery may also be applied within the scope of the invention,
particularly when adapted to deliver gas at multiple intermediate
delivery pressures and/or to intake gas at multiple intermediate
inlet pressures. The invention enables use of single shaft machines
to provide all compression and expansion functions for a plurality
of modules in parallel, as well as the combined use of motor driven
and free rotor machines for more flexible modularization and
splitting of stages.
[0018] The inventive concept of split stream centrifugal machinery
is a desirable option for the described PSA process which requires
various enthalpies in separate fluid streams at differing total
pressures. The split stream machine has multiple inlet flows at
multiple enthalpies, and/or multiple exit flows at multiple
enthalpies, for a single centrifugal or radial flow impeller. The
differing changes in enthalpy or total pressure are achieved by
having a different change in radius, or differing blade angles, for
each flow across the impeller. A split stream compressor has one
inlet but numerous outlets at different total pressures or enthalpy
levels from a single impeller. A split stream exhauster may be a
vacuum pump or an expander, and will have multiple inlets and a
single outlet at different total pressures or enthalpy levels for a
single impeller. Also useful in the present invention is a split
stream light reflux expander having a number of inlets and the same
number of outlets, at different total pressures or enthalpy levels
for a single impeller.
BRIEF DESCRIPTION OF THE DRAWINGS
[0019] The preferred embodiments of the present invention will now
be described, by way of example only, and with reference to the
drawings, in which like reference numerals indicate like elements,
and in which:
[0020] FIG. 1 is a sectional view of a rotary PSA module according
to the invention;
[0021] FIG. 2 is the stator of the module of FIG. 1;
[0022] FIG. 3 is the rotor of the module of FIG. 1;
[0023] FIG. 4 is an axial section of the module of FIG. 1;
[0024] FIG. 5 shows an alternative adsorber configuration using
layered adsorbent sheets;
[0025] FIG. 6 shows a typical PSA cycle according to the
invention;
[0026] FIG. 7 shows a PSA cycle with heavy reflux;
[0027] FIG. 8 shows a PSA apparatus with a single rotary module and
energy recovery;
[0028] FIG. 9 shows a vacuum PSA (VPSA) for oxygen separation from
air;
[0029] FIG. 10 shows a VPSA apparatus without light reflux energy
recovery;
[0030] FIG. 11 shows a PSA apparatus adapted to receive two feed
gas mixtures, and with recompression of tail gas;
[0031] FIG. 12 shows a PSA apparatus with heavy reflux;
[0032] FIG. 13 shows a PSA apparatus with a free rotor tail gas
compressor or vacuum pump, powered by energy recovery;
[0033] FIG. 14 shows another embodiment of a PSA apparatus with a
free rotor compressor;
[0034] FIG. 15 shows a VPSA apparatus with 4 modules;
[0035] FIG. 16 shows a PSA apparatus with 5 modules;
[0036] FIG. 17 shows a simplified schematic of a VPSA cycle for
oxygen production, using a split stream air compressor, a split
stream vacuum pump as the countercurrent blowdown exhauster, and a
split stream light reflux expander powering a product oxygen
compressor;
[0037] FIG. 18 shows a radial flow rotary PSA module;
[0038] FIG. 19 shows an axial flow rotary PSA module;
[0039] FIG. 20 shows a double axial flow rotary PSA module;
[0040] FIG. 21 shows the first valve face of the embodiment of FIG.
19;
[0041] FIG. 22 shows the second valve face of the embodiment of
FIG. 19;
[0042] FIG. 23 shows an adsorber wheel configurations based on
laminated adsorbent sheet adsorbers for the embodiment of FIG.
19;
[0043] FIG. 24 shows a multistage centrifugal compressor with
impulse turbine expanders for the light reflux and countercurrent
blowdown;
[0044] FIG. 25 shows the light reflux impulse turbine runner with
four nozzles;
[0045] FIG. 26 is an unrolled view of the light reflux expander
impulse turbine;
[0046] FIG. 27 is an unrolled view of the countercurrent blowdown
expander impulse turbine;
[0047] FIG. 28 shows a split stream axial compressor with three
stages; and
[0048] FIG. 29 shows a composite pellet with zeolite material
coated on a high specific gravity inert core, for centrifugally
stabilized granular adsorbers in radial flow embodiments.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
[0049] FIGS. 1, 2, 3 and 4
[0050] A rotary module 10 according to the invention is shown in
FIGS. 1, 2, 3 and 4. The module includes a rotor 11 revolving about
axis 12 in the direction shown by arrow 13 within stator 14. FIG. 4
is an axial section of the module 10, defined by arrows 15 and 16
in FIG. 1. FIG. 1 is a cross-section of the module 10, defined by
arrows 17 and 18 in FIG. 4. FIG. 2 is the sectional view of the
rotor 11 repeated from FIG. 1, with the stator deleted for clarity.
FIG. 3 is the sectional view of the stator 14 repeated from FIG. 1,
with details of the rotor deleted for clarity.
[0051] In general, the apparatus of the invention may be configured
for flow through the adsorber elements in the radial, axial or
oblique conical directions relative to the rotor axis. For
operation at high cycle frequency, radial flow has the advantage
that the centripetal acceleration will lie parallel to the flow
path for most favourable stabilization of buoyancy-driven free
convection, as well as centrifugal clamping of granular adsorbent
with uniform flow distribution. As shown in FIG. 2, the rotor 11 is
of annular section, having concentrically to axis 12 an outer
cylindrical wall 20 whose external surface is first valve surface
21, and an inner cylindrical wall 22 whose internal surface is
second valve surface 23. The rotor has (in the plane of the section
defined by arrows 15 and 16 in FIG. 4) a total of "N" radial flow
adsorber elements 24. An adjacent pair of adsorber elements 25 and
26 are separated by partition 27 which is structurally and
sealingly joined to outer wall 20 and inner wall 22. Adjacent
adsorber elements 25 and 26 are angularly spaced relative to axis
12 by an angle of [360.degree./N].
[0052] Adsorber element 24 has a first end 30 defined by support
screen 31 and a second end 32 defined by support screen 33. The
adsorber may be provided as granular adsorbent, whose packing
voidage defines a flow path contacting the adsorbent between the
first and second ends of the adsorber.
[0053] First aperture or orifice 34 provides flow communication
from first valve surface 21 through wall 20 to the first end 30 of
adsorber 24. Second aperture or orifice 35 provides flow
communication from second valve surface 23 through wall 22 to the
second end 31 of adsorber 24. Support screens 31 and 33
respectively provide flow distribution 32 between first aperture 34
and first end 30, and between second aperture 35 and second end 32,
of adsorber element 24. Support screen 31 also supports the
centrifugal force loading of the adsorbent.
[0054] As shown in FIG. 3, stator 14 is a pressure housing
including an outer cylindrical shell or first valve stator 40
outside the annular rotor 11, and an inner cylindrical shell or
second valve stator 41 inside the annular rotor 11. Outer shell 40
carries axially extending strip seals (e.g. 42 and 43) sealingly
engaged with first valve surface 21, while inner shell 41 carries
axially extending strip seals (e.g. 44 and 45) sealingly engaged
with second valve surface 23. The azimuthal sealing width of the
strip seals is greater than the diameters or azimuthal widths of
the first and second apertures 34 and 35 opening through the first
and second valve surfaces.
[0055] A set of first compartments in the outer shell each open in
an angular sector to the first valve surface, and each provide
fluid communication between its angular sector of the first valve
surface and a manifold external to the module. The angular sectors
of the compartments are much wider than the angular separation of
the adsorber elements. The first compartments are separated on the
first sealing surface by the strip seals (e.g. 42). Proceeding
clockwise in FIG. 3, in the direction of rotor rotation, a first
feed pressurization compartment 46 communicates by conduit 47 to
first feed pressurization manifold 48, which is maintained at a
first intermediate feed pressure. Similarly, a second feed
pressurization compartment 50 communicates to second feed
pressurization manifold 51, which is maintained at a second
intermediate feed pressure higher than the first intermediate feed
pressure but less than the higher working pressure.
[0056] For greater generality, module 10 is shown with provision
for sequential admission of two feed mixtures, the first feed gas
having a lower concentration of the more readily adsorbed component
relative to the second feed gas. First feed compartment 52
communicates to first feed manifold 53, which is maintained at
substantially the higher working pressure. Likewise, second feed
compartment 54 communicates to second feed manifold 55, which is
maintained at substantially the higher working pressure. A first
countercurrent blowdown compartment 56 communicates to first
countercurrent blowdown manifold 57, which is maintained at a first
countercurrent blowdown intermediate pressure. A second
countercurrent blowdown compartment 58 communicates to second
countercurrent blowdown manifold 59, which is maintained at a
second countercurrent blowdown intermediate pressure above the
lower working pressure. A heavy product compartment 60 communicates
to heavy product exhaust manifold 61 which is maintained at
substantially the lower working pressure. It will be noted that
compartment 58 is bounded by strip seals 42 and 43, and similarly
all the compartments are bounded and mutually isolated by strip
seals.
[0057] A set of second compartments in the inner shell each open in
an angular sector to the second valve surface, and each provide
fluid communication between its angular sector of the second valve
surface and a manifold external to the module. The second
compartments are separated on the second sealing surface by the
strip seals (e.g. 44). Proceeding clockwise in FIG. 3, again in the
direction of rotor rotation, light product compartment 70
communicates to light product manifold 71, and receives light
product gas at substantially the higher working pressure, less
frictional pressure drops through the adsorbers and the first and
second orifices. According to the angular extension of compartment
70 relative to compartments 52 and 54, the light product may be
obtained only from adsorbers simultaneously receiving the first
feed gas from compartment 52, or from adsorbers receiving both the
first and second feed gases.
[0058] A first light reflux exit compartment 72 communicates to
first light reflux exit manifold 73, which is maintained at a first
light reflux exit pressure, here substantially the higher working
pressure less frictional pressure drops. A first cocurrent blowdown
compartment 74 (which is actually the second light reflux exit
compartment), communicates to second light reflux exit manifold 75,
which is maintained at a first cocurrent blowdown pressure less
than the higher working pressure. A second cocurrent blowdown
compartment or third light reflux exit compartment 76 communicates
to third light reflux exit manifold 77, which is maintained at a
second cocurrent blowdown pressure less than the first cocurrent
blowdown pressure. A third cocurrent blowdown compartment or fourth
light reflux exit compartment 78 communicates to fourth light
reflux exit manifold 79, which is maintained at a third cocurrent
blowdown pressure less than the second cocurrent blowdown
pressure.
[0059] A purge compartment 80 communicates to a fourth light reflux
return manifold 81, which supplies the fourth light reflux gas
which has been expanded from the third cocurrent blowdown pressure
to substantially the lower working pressure with an allowance for
frictional pressure drops. The ordering of light reflux
pressurization steps is inverted from the ordering or light reflux
exit or cocurrent blowdown steps, so as to maintain a desirable
"last out-first in" stratification of light reflux gas packets.
Hence a first light reflux pressurization compartment 82
communicates to a third light reflux return manifold 83, which
supplies the third light reflux gas which has been expanded from
the second cocurrent blowdown pressure to a first light reflux
pressurization pressure greater than the lower working pressure. A
second light reflux pressurization compartment 84 communicates to a
second light reflux return manifold 85, which supplies the second
light reflux gas which has been expanded from the first cocurrent
blowdown pressure to a second light reflux pressurization pressure
greater than the first light reflux pressurization pressure.
Finally, a third light reflux pressurization compartment 86
communicates to a first light reflux return manifold 87, which
supplies the first light reflux gas which has been expanded from
approximately the higher pressure to a third light reflux
pressurization pressure greater than the second light reflux
pressurization pressure, and in this example less than the first
feed pressurization pressure.
[0060] Additional details are shown in FIG. 4. Conduits 88 connect
first compartment 60 to manifold 61, with multiple conduits
providing for good axial flow distribution in compartment 60.
Similarly, conduits 89 connect second compartment 80 to manifold
81. Stator 14 has base 90 with bearings 91 and 92. The annular
rotor 11 is supported on end disc 93, whose shaft 94 is supported
by bearings 91 and 92. Motor 95 is coupled to shaft 94 to drive
rotor 11. The rotor could alternatively rotate as an annular drum,
supported by rollers at several angular positions about its rim and
also driven at its rim so that no shaft would be required. A rim
drive could be provided by a ring gear attached to the rotor, or by
a linear electromagnetic motor whose stator would engage an arc of
the rim. Outer circumferential seals 96 seal the ends of outer
strip seals 42 and the edges of first valve surface 21, while inner
circumferential seals 97 seal the ends of inner strip seals 44 and
the edges of second valve surface 23. Rotor 11 has access plug 98
between outer wall 20 and inner wall 22, which provides access for
installation and removal of the adsorbent in adsorbers 24.
[0061] A further most important benefit of the invention in radial
flow embodiments arises in purification of very low molecular
weight gases such as hydrogen and helium to remove higher molecular
weight impurities. Here, the light product is separated radially
inward, while the heavy impurities are separated radially outward
by the centrifugal PSA apparatus of the present invention. In all
PSA systems, dispersive effects including axial dispersion, uneven
bed packing, thermal gradients and wall flow channeling all tend to
spread the concentration gradient in the bed so as to degrade
separation performance. But the strong centripetal acceleration
field of the present invention will induce a buoyant stratification
of the purified light fraction radially inward of the separated
heavy fraction, thus opposing dispersive effects and enhancing
separation performance. This important desirable effect is present
whether granular adsorbent or laminated sheet supported adsorbent
is used, as along as the flow direction in the adsorbent bed is
radially inward from the first end to the second end of the
bed.
[0062] In air separation with the feed presented to the outer
radius of the adsorbers, the buoyancy effect due to the greater
molecular weight of oxygen compared to nitrogen would be modestly
adverse. The molecular weight difference between hydrogen and its
impurities (other than helium) is far greater and in the desired
direction. Some process embodiments of the present invention
include the feature of heating the oxygen light reflux gas, for the
main objects of thermally enhancing expansion energy recovery,
improving adsorption/desorption kinetics, and shifting the optimal
operating pressure range from vacuum to positive superatmospheric
pressure conditions. Heating the light reflux oxygen sufficiently
will create a radial thermal gradient, so that the second end of
the adsorbers (at an inner radius) will be hotter than the first
end of the adsorbers (at an outer radius). In a rapidly rotating
rotor of the invention, this thermal gradient will enhance the
convective stability of the mass transfer front in the adsorbers,
and will tend to compensate the adverse effect of oxygen being more
dense than nitrogen at equal temperature. The present invention
thus can provide radial stabilization of the mass transfer front by
establishing a radial density gradient either of lower molecular
weight of the gas contacting the adsorbent radially inward, or by a
thermal gradient of higher temperature radially inward.
[0063] Alternatively, convective stability in air separation
applications may be enhanced by operating with the feed applied to
an inner radius of radial flow rotating adsorbers, while the oxygen
as second product is withdrawn from an outer radius.
[0064] FIG. 5
[0065] An attractive alternative to the use of granular adsorbent
is obtained by forming the adsorbent material with a suitable
reinforcement matrix into thin adsorbent sheets, and layering the
adsorbent sheets with spacers to form a layered sheet contactor
with flow channels between adjacent pairs of sheets. The adsorber
elements may then be installed as angularly spaced rectangular
blocks within the rotor and between the first and second valve
faces, with the adsorbent sheets as substantially flat sheets
extending parallel to the plane defined by the axis of the rotor
and a radius from the axis through the rectangular block, and the
flat adsorbent sheets being layered with flow channels between them
to form the rectangular block. The flow channels also lie in planes
parallel to the sheets and to the plane defined by the axis of the
rotor and a radius from the axis through the rectangular blocks,
and may be configured for either axial flow or radial flow. In the
axial flow case, the first and second valve surfaces would be
provided as flat discs perpendicular to and concentric with the
axis of rotation. In the radial flow case, represented by FIGS.
1-4, the first and second valve surfaces are provided as inner and
outer cylindrical surfaces bounding the annular rotor within which
the adsorber elements are mounted.
[0066] A section 110 of rotor 11 has been identified in FIG. 2
between the curved lines with endpoints 111 and 112, and 113 and
114. FIG. 5 shows section 110 in detail, with the laminated sheet
embodiment of the adsorbers.
[0067] The laminate sheets 115 lie in the radial plane and are
layered to form the adsorber elements 24 as rectangular blocks.
Each sheet 115 comprises reinforcement material, e.g. a glass fiber
or metal wire matrix (woven or non-woven) on which the adsorbent
material (e.g. zeolite crystallites is supported by a suitable
binder (e.g., clay, silicate or coke binders). Typical thickness of
an adsorbent sheet may be about 100 microns. The sheets 115 are
installed with spacers on one or both sides to establish flow
channels between adjacent pairs of sheets. The flow channels define
the flow path approximately in the radial direction between first
end 30 and second end 32 of the flow path in each adsorber element.
Typical channel height would be about 50% to 100% of the adsorbent
sheet thickness.
[0068] The adsorbent sheets comprise a reinforcement material,
preferably glass fibre, but alternatively metal foil or wire mesh,
to which the adsorbent material is attached with a suitable binder.
For air separation to produce enriched oxygen, typical adsorbents
are X, A or chabazite type zeolites, typically exchanged with
calcium or lithium cations. The zeolite crystals are bound with
silica, clay and other binders within the adsorbent sheet
matrix.
[0069] Satisfactory adsorbent sheets have been made by coating a
slurry of zeolite crystals with binder constituents onto the
reinforcement material, with successful examples including
non-woven fiber glass scrims, woven metal fabrics, and expanded
aluminum foils. Spacers are provided by printing or embossing the
adsorbent sheet with a raised pattern, or by placing a fabricated
spacer between adjacent pairs of adsorbent sheets. Alternative
satisfactory spacers have been provided as woven metal screens,
fiber glass scrims, and metal foils with etched flow channels in a
photolithographic pattern.
[0070] Typical experimental sheet thicknesses have been 150
microns, with spacer heights in the range of 100 to 150 microns,
and adsorber flow channel length approximately 20 cm. Using X type
zeolites, excellent performance has been achieved in oxygen
separation from air at PSA cycle frequencies in the range of 50 to
100 cycles per minute.
[0071] FIGS. 6 and 7
[0072] FIG. 6 shows a typical PSA cycle according to the invention,
while FIG. 7 shows a similar PSA cycle with heavy reflux
recompression of a portion of the first product gas to provide a
second feed gas to the process.
[0073] In FIGS. 6 and 7, the vertical axis 150 indicates the
working pressure in the adsorbers and the pressures in the first
and second compartments. Pressure drops due to flow within the
adsorber elements are neglected. The higher and lower working
pressures are respectively indicated by dotted lines 151 and
152.
[0074] The horizontal axis 155 of FIGS. 6 and 7 indicates time,
with the PSA cycle period defined by the time interval between
points 156 and 157. At times 156 and 157, the working pressure in a
particular adsorber is pressure 158. Starting from time 156, the
cycle for a particular adsorber (e.g. 24) begins as the first
aperture 34 of that adsorber is opened to the first feed
pressurization compartment 46, which is fed by first feed supply
means 160 at the first intermediate feed pressure 161. The pressure
in that adsorber rises from pressure 158 at time 157 to the first
intermediate feed pressure 161. Proceeding ahead, first aperture
passes over a seal strip, first closing adsorber 24 to compartment
46 and then opening it to second feed pressurization compartment 50
which is feed by second feed supply means 162 at the second
intermediate feed pressure 163. The adsorber pressure rises to the
second intermediate feed pressure.
[0075] First aperture 34 of adsorber 24 is opened next to first
feed compartment 52, which is maintained at substantially the
higher pressure by a third feed supply means 165. Once the adsorber
pressure has risen to substantially the higher working pressure,
its second aperture 35 (which has been closed to all second
compartments since time 156) opens to light product compartment 70
and delivers light product 166.
[0076] In the cycle of FIG. 7, first aperture 34 of adsorber 24 is
opened next to second feed compartment 54, also maintained at
substantially the higher pressure by a fourth feed supply means
167. In general, the fourth feed supply means supplies a second
feed gas, typically richer in the more readily adsorbed component
than the first feed gas provided by the first, second and third
feed supply means. In the specific cycle illustrated in FIG. 7, the
fourth feed supply means 167 is a "heavy reflux" compressor,
recompressing a portion of the heavy product back into the
apparatus. In the cycle illustrated in FIG. 6, there is no fourth
feed supply means, and compartment 54 could be eliminated or
consolidated with compartment 52 extended over a wider angular arc
of the stator.
[0077] While feed gas is still being supplied to the first end of
adsorber 24 from either compartment 52 or 54, the second end of
adsorber 24 is closed to light product compartment 70 and opens to
first light reflux exit compartment 72 while delivering "light
reflux" gas (enriched in the less readily adsorbed component,
similar to second product gas) to first light reflux pressure
let-down means (or expander) 170. The first aperture 34 of adsorber
24 is then closed to all first compartments, while the second
aperture 35 is opened successively to (a) second light reflux exit
compartment 74, dropping the adsorber pressure to the first
cocurrent blowdown pressure 171 while delivering light reflux gas
to second light reflux pressure letdown means 172, (b) third light
reflux exit compartment 76, dropping the adsorber pressure to the
second cocurrent blowdown pressure 173 while delivering light
reflux gas to third light reflux pressure letdown means 174, and
(c) fourth light reflux exit compartment 78, dropping the adsorber
pressure to the third cocurrent blowdown pressure 175 while
delivering light reflux gas to fourth light reflux pressure letdown
means 176. Second aperture 35 is then closed for an interval, until
the light reflux return steps following the countercurrent blowdown
steps.
[0078] The light reflux pressure let-down means may be mechanical
expanders or expansion stages for expansion energy recovery, or may
be restrictor orifices or throttle valves for irreversible pressure
let-down.
[0079] Either when the second aperture is closed after the final
light reflux exit step (as shown in FIGS. 6 and 7), or earlier
while light reflux exit steps are still underway, first aperture 34
is opened to first countercurrent blowdown compartment 56, dropping
the adsorber pressure to the first countercurrent blowdown
intermediate pressure 180 while releasing "heavy" gas (enriched in
the more strongly adsorbed component) to first exhaust means 181.
Then, first aperture 34 is opened to second countercurrent blowdown
compartment 58, dropping the adsorber pressure to the first
countercurrent blowdown intermediate pressure 182 while releasing
heavy gas to second exhaust means 183. Finally reaching the lower
working pressure, first aperture 34 is opened to heavy product
compartment 60, dropping the adsorber pressure to the lower
pressure 152 while releasing heavy gas to third exhaust means 184.
Once the adsorber pressure has substantially reached the lower
pressure while first aperture 34 is open to compartment 60, the
second aperture 35 opens to purge compartment 80, which receives
fourth light reflux gas from fourth light reflux pressure let-down
means 176 in order to displace more heavy gas into first product
compartment 60.
[0080] In FIG. 6, the heavy gas from the first, second and third
exhaust means is delivered as the heavy product 185. In FIG. 7,
this gas is partly released as the heavy product 185, while the
balance is redirected as "heavy reflux" 187 to the heavy reflux
compressor as fourth feed supply means 167. Just as light reflux
enables an approach to high purity of the less readily adsorbed
("light") component in the light product, heavy reflux enables an
approach to high purity of the more readily adsorbed ("heavy")
component in the heavy product.
[0081] The adsorber is then repressurized by light reflux gas after
the first and second apertures close to compartments 60 and 80. In
succession, while the first aperture 34 remains closed at least
initially, (a) the second aperture 35 is opened to first light
reflux pressurization compartment 82 to raise the adsorber pressure
to the first light reflux pressurization pressure 190 while
receiving third light reflux gas from the third light reflux
pressure letdown means 174, (b) the second aperture 35 is opened to
second light reflux pressurization compartment 84 to raise the
adsorber pressure to the second light reflux pressurization
pressure 191 while receiving second light reflux gas from the
second light reflux pressure letdown means 172, and (c) the second
aperture 35 is opened to third light reflux pressurization
compartment 86 to raise the adsorber pressure to the third light
reflux pressurization pressure 192 while receiving first light
reflux gas from the first light reflux pressure letdown means 170.
Unless feed pressurization has already been started while light
reflux return for light reflux pressurization is still underway,
the process (as based on FIGS. 6 and 7) begins feed pressurization
for the next cycle after time 157 as soon as the third light reflux
pressurization step has been concluded.
[0082] The pressure variation waveform in each adsorber would be a
rectangular staircase if there were no throttling in the first and
second valves. In order to provide balanced performance of the
adsorbers, preferably all of the apertures are closely identical to
each other.
[0083] The rate of pressure change in each pressurization or
blowdown step will be restricted by throttling in ports (or in
clearance or labyrinth sealing gaps) of the first and second valve
means, or by throttling in the apertures at first and second ends
of the adsorbers, resulting in the typical pressure waveform
depicted in FIGS. 6 and 7. Alternatively, the apertures may be
opened slowly by the seal strips, to provide flow restriction
throttling between the apertures and the seal strips, which may
have a serrated edge (e.g. with notches or tapered slits in the
edge of the seal strip) so that the apertures are only opened to
full flow gradually. Excessively rapid rates of pressure change
would subject the adsorber to mechanical stress, while also causing
flow transients which would tend to increase axial dispersion of
the concentration wavefront in the adsorber. Pulsations of flow and
pressure are minimized by having a plurality of adsorbers
simultaneously transiting each step of the cycle, and by providing
enough volume in the function compartments and associated manifolds
so that they act effectively as surge absorbers between the
compression machinery and the first and second valve means.
[0084] It will be evident that the cycle could be generalized by
having more or fewer intermediate stages in each major step of feed
pressurization, countercurrent blowdown exhaust, or light reflux.
Furthermore, in air separation or air purification applications, a
stage of feed pressurization (typically the first stage) could be
performed by equalization with atmosphere as an intermediate
pressure of the cycle. Similarly, a stage of countercurrent
blowdown could be performed by equalization with atmosphere as an
intermediate pressure of the cycle.
[0085] FIG. 8
[0086] FIGS. 8-15 are simplified schematics of PSA systems using
the module 10 of FIGS. 1-4 as the basic building block, and showing
the connections from the first and second manifolds of the module
to machinery for compression and expansion of gases in typical
applications. In FIGS. 8-15, the reference numerals of the first
and second manifolds are as defined for FIG. 3.
[0087] FIG. 8 is a simplified schematic of a PSA system for
separating oxygen from air, using nitrogen-selective zeolite
adsorbents. The light product is concentrated oxygen, while the
heavy product is nitrogen-enriched air usually vented as waste. The
cycle lower pressure 152 is nominally atmospheric pressure. Feed
air is introduced through filter intake 200 to a feed compressor
201. The feed compressor includes compressor first stage 202,
intercooler 203, compressor second stage 204, second intercooler
205, compressor third stage 206, third intercooler 207, and
compressor fourth stage 208. The feed compressor 201 as described
may be a four stage axial compressor or centrifugal compressor with
motor 209 as prime mover coupled by shaft 210, and the intercoolers
are optional. With reference to FIG. 6, the feed compressor first
and second stages are the first feed supply means 160, delivering
feed gas at the first intermediate feed pressure 161 via conduit
212 and water condensate separator 213 to first feed pressurization
manifold 48. Feed compressor third stage 206 is the second feed
supply means 162, delivering feed gas at the second intermediate
feed pressure 163 via conduit 214 and water condensate separator
215 to second feed pressurization manifold 51. Feed compressor
fourth stage 208 is the third feed supply means 165, delivering
feed gas at the higher pressure 151 via conduit 216 and water
condensate separator 217 to feed manifold 53. Light product oxygen
flow is delivered from light product manifold 71 by conduit 218,
maintained at substantially the higher pressure less frictional
pressure drops.
[0088] The apparatus of FIG. 8 includes energy recovery expanders,
including light reflux expander 220 (here including four stages)
and countercurrent blowdown expander 221 (here including two
stages), coupled to feed compressor 201 by shaft 222. The expander
stages may be provided for example as radial inflow turbine stages,
as full admission axial turbine stages with separate wheels, or as
partial admission impulse turbine stages combined in a single wheel
as illustrated in FIGS. 17-20 below.
[0089] Light reflux gas from first light reflux exit manifold 73
flows at the higher pressure via conduit 224 and heater 225 to
first light pressure letdown means 170 which here is first light
reflux expander stage 226, and then flows at the third light reflux
pressurization pressure 192 by conduit 227 to the first light
reflux return manifold 87. Light reflux gas from second light
reflux exit manifold 75 flows at the first cocurrent blowdown
pressure 171 via conduit 228 and heater 225 to second light reflux
pressure letdown means 172, here the second expander stage 230, and
then flows at the second light reflux pressurization pressure 191
by conduit 231 to the second light reflux return manifold 85. Light
reflux gas from third light reflux exit manifold 77 flows at the
second cocurrent blowdown pressure 173 via conduit 232 and heater
225 to third light reflux pressure letdown means 174, here the
third expander stage 234, and then flows at the first light reflux
pressurization pressure 190 by conduit 235 to the third light
reflux return manifold 83. Finally, light reflux gas from fourth
light reflux exit manifold 79 flows at the third cocurrent blowdown
pressure 175 via conduit 236 and heater 225 to fourth light reflux
pressure letdown means 176, here the fourth light reflux expander
stage 238, and then flows at substantially the lower pressure 152
by conduit 239 to the fourth light reflux return manifold 81.
[0090] Heavy countercurrent blowdown gas from first countercurrent
blowdown manifold 57 flows at first countercurrent blowdown
intermediate pressure 180 by conduit 240 to heater 241 and thence
to first stage 242 of the countercurrent blowdown expander 221 as
first exhaust means 181, and is discharged from the expander to
exhaust manifold 243 at substantially the lower pressure 152.
Countercurrent blowdown gas from second countercurrent blowdown
manifold 59 flows at second countercurrent blowdown intermediate
pressure 182 by conduit 244 to heater 241 and thence to second
stage 245 of the countercurrent blowdown expander 221 as second
exhaust means 183, and is discharged from the expander to exhaust
manifold 243 at substantially the lower pressure 152. Finally,
heavy gas from heavy product exhaust manifold 61 flows by conduit
246 as third exhaust means 184 to exhaust manifold 243 delivering
the heavy product gas 185 to be vented at substantially the lower
pressure 152.
[0091] Heaters 225 and 241 raise the temperatures of gases entering
expanders 220 and 221, thus augmenting the recovery of expansion
energy and increasing the power transmitted by shaft 222 from
expanders 220 and 221 to feed compressor 201, and reducing the
power required from prime mover 209. While heaters 225 and 241 are
means to provide heat to the expanders, intercoolers 203, 205 and
207 are means to remove heat from the feed compressor and serve to
reduce the required power of the higher compressor stages. The
haters and intercoolers are optional features of the invention.
[0092] If light reflux heater 249 operates at a sufficiently high
temperature so that the exit temperature of the light reflux
expansion stages is higher than the temperature at which feed gas
is delivered to the feed manifolds by conduits 212, 214 and 216,
the temperature of the second ends 35 of the adsorbers 24 may be
higher than the temperature of their first ends 34. Hence, the
adsorbers have a thermal gradient along the flow path, with higher
temperature at their second end relative to the first end. This is
an extension of the principle of "thermally coupled pressure swing
adsorption" (TCPSA), introduced by Keefer in U.S. Pat. No.
4,702,903. Adsorber rotor 11 then acts as a thermal rotary
regenerator, as in regenerative gas turbine engines having a
compressor 201 and an expander 220. Heat provided to the PSA
process by heater 225 assists powering the process according to a
regenerative thermodynamic power cycle, similar to advanced
regenerative gas turbine engines approximately realizing the
Ericsson thermodynamic cycle with intercooling on the compression
side and interstage heating on the expansion side.
[0093] In the instance of PSA applied to oxygen separation from
air, the total light reflux flow is much less than the feed flow
because of the strong bulk adsorption of nitrogen. Accordingly the
power recoverable from the expanders is much less than the power
required by the compressor, but will still contribute significantly
to enhanced efficiency of oxygen production. By operating the
adsorbers at moderately elevated temperature and using strongly
nitrogen-selective adsorbents such as Ca--X, Li--X or calcium
chabazite zeolites, a PSA oxygen generation system can operate with
favourable performance and exceptional efficiency. While higher
temperature of the adsorbent will reduce nitrogen uptake and
selectivity, the isotherms will be more linear. Effective working
capacity in superatmospheric pressure PSA cycles may be enhanced by
operation in TCPSA mode with an elevated temperature gradient in
the adsorbers. Working with adsorbents such as Ca--X and Li--X,
recent conventional practice has been to operate ambient
temperature PSA at subatmospheric lower pressures in so-called
"vacuum swing adsorption" (VSA), so that the highly selective
adsorbents operate well below saturation in nitrogen uptake, and
have a large working capacity in a relatively linear isotherm
range. At higher temperatures, saturation in nitrogen uptake is
shifted to more elevated pressures, so the optimum PSA cycle higher
and lower pressures are also shifted upward. For satisfactory
operation of the apparatus of FIG. 8, the typical operating
temperature of the second ends of the adsorbers may be
approximately 50.degree. C. for Ca--X or Li--X, and 100.degree. to
150.degree. C. for calcium chabazite.
[0094] If high energy efficiency were not of highest importance,
the light reflux expander stages and the countercurrent blowdown
expander stages could be replaced by restrictor orifices or
throttle valves for pressure letdown, as illustrated in FIG. 10.
The schematic of FIG. 8 shows a single shaft supporting the
compressor stages, the countercurrent blowdown or exhaust expander
stages, and the light reflux stages, as well as coupling the
compressor to the prime mover. However, it should be understood
that separate shafts and even separate prime movers may be used for
the distinct compression and expansion stages within the scope of
the present invention.
[0095] It should also be understood that the number of compression
stages and the number of expansion stages (as well as the number of
vacuum pump stages in the embodiment of FIG. 9 below) may be varied
within the scope of the invention. Generally and for equal stage
efficiency of the compressor or expander type chosen, a larger
number of stages will improve the PSA process efficiency, since the
irreversible equalization expansions over the first and second
orifices will be performed over narrower pressure intervals.
However, the improvement in efficiency for each additional stage
will diminish as the number of stages is greater.
[0096] FIG. 9
[0097] FIG. 9 shows a vacuum PSA (VPSA) system for oxygen
separation from air. Intermediate pressure 158 of FIG. 6 is now
nominally atmospheric pressure. Lower pressure 152 and higher
pressure 151 may respectively be approximately 0.5 and 1.5 times
atmospheric pressure. Feed compressor first stage 202 becomes
directly the first feed means feeding manifold 48. Likewise,
compressor second stage 204 and third stage 206 operate as the
second feed means 162 and third feed means 165 respectively. The
condensate separators are omitted for simplicity.
[0098] A multistage vacuum pump 260 is driven by shaft 222, and
assisted by light reflux expander 220. The vacuum pump may for
example be a multistage centrifugal or axial compression machine,
or it may be provided by rotary positive displacement machinery
adapted to accept inlet gas at multiple suction pressures. First
stage vacuum pump 261 (acting as third exhaust means 184) draws
nitrogen-enriched air from the heavy product exhaust manifold 61 at
substantially the lower pressure, and delivers this gas through
intercooler 262 at the second countercurrent blowdown pressure 182
to second stage vacuum pump 263 (acting as second exhaust means
182) which also draws heavy gas from the second countercurrent
blowdown manifold 59 at the same pressure. The combined heavy gas
discharged from vacuum pump 260 is combined with heavy gas
discharged by conduit 240 (acting as first exhaust means 181) to
form the heavy product 185 delivered to atmosphere (equal to the
first countercurrent blowdown pressure) by conduit 243.
[0099] FIG. 10
[0100] FIG. 10 shows a VPSA apparatus similar to that of FIG. 9,
but with the light reflux pressure letdown means 170, 172, 174 and
176 provided respectively by throttle orifices 270, 272, 274, and
276. The throttle orifices may be fixed orifices, or may be
throttle valves with a control actuator 277 for coordinated
adjustment of their orifice aperture. Control actuator 277 provides
means to adjust the rate of pressure letdown for each light reflux
step, so that the process may be adjusted for operation at a
different cycle frequency or a different ratio of the higher and
lower working pressures. It should be noted that adjustable nozzles
(similar to the above adjustable throttles with controller 277) may
be alternatively used in conjunction with expansion turbines used
for each of the light reflux (or countercurrent blowdown expander
stages.
[0101] FIG. 11
[0102] FIG. 11 shows a PSA apparatus adapted to receive two feed
gas mixtures, and with recompression of the heavy product gas. A
suitable application would be hydrogen recovery from petroleum
refinery offgases, e.g. hydrotreater purge gases typically
containing light hydrocarbon gases with 30% to 70% hydrogen.
Frequently, several offgases of differing hydrogen concentration
are available at elevated feed pressures in the range of 10 to 20
atmospheres. Using typical adsorbents, e.g. activated carbon or
zeolites, the hydrocarbon impurities will be much more readily
adsorbed than hydrogen, so the purified hydrogen will be the light
product delivered at the higher working pressure which may be only
slightly less than the feed supply pressure, while the impurities
will be concentrated as the heavy product and will be exhausted
from the PSA process as "PSA tail gas" at the lower working
pressure. The tail gas is often either flared or used as fuel
gas.
[0103] For hydrogen duty, positive displacement expansion and
compression machinery (e.g. twin screw machines) may be preferred
because of the low molecular weight of the gas. Such machines may
be adapted in accordance with the invention with extra inlet and/or
discharge ports to accept and deliver gas at multiple intermediate
pressures.
[0104] Performance and productivity of PSA hydrogen recovery from
refinery offgases (with the adsorbers working at near ambient
temperature) will be greatly enhanced by operating with the lower
working pressure as low as possible and preferably near atmospheric
pressure. However, the tail gas is usually delivered at a pressure
of at least 5 or 6 atmospheres, for disposal to the refinery fuel
gas header. Compression costs, particularly for combustible gases
under refinery safety constraints, may be prohibitively high.
[0105] The apparatus of FIG. 11 is configured to accept first and
second feed gas mixtures, the first having a higher concentration
of the less readily adsorbed component (e.g. hydrogen) while the
second is more concentrated than the first feed gas mixture in the
more readily adsorbed fraction. The first feed gas is supplied at
substantially the higher working pressure by first infeed conduit
280 to first feed manifold 53, while the second feed gas is
supplied at substantially the higher working pressure by second
infeed conduit 281 to first feed manifold 55. Each adsorber
receives the second feed gas after receiving the first feed gas, so
that the concentration profile in the adsorber is monotonically
declining in concentration of the more readily adsorbed component
along its flow path from first end 34 to second end 35 of the flow
path in adsorber element 24. All but the final pressurization steps
are here achieved with light reflux gas. The final feed
pressurization (from the third light reflux pressurization pressure
192 directly to the higher pressure 151) is achieved as the first
end of each adsorber is opened to compartment 52 communicating to
manifold 53. Additional feed pressurization steps could readily be
incorporated as in the embodiment of FIG. 8.
[0106] In this embodiment, the tail gas (heavy product) is
discharged from second product delivery conduit at a higher
pressure than the lower working pressure, in this example being
approximately the first countercurrent blowdown pressure 180 of
FIG. 6 with conduit 240 being first exhaust means 181. Tail gas is
recompressed by tail gas compressor 290, with compressor first
stage 291 being the third exhaust means 184 compressing the first
product gas from exhaust manifold 61 via conduit 246, and
delivering the first product gas after first stage compression
through intercooler 292 to compressor second stage 293 which itself
is the second exhaust means compressing second countercurrent
blowdown gas from manifold 59 via conduit 244.
[0107] FIG. 12
[0108] FIG. 12 shows a PSA apparatus with heavy reflux to obtain
either higher enrichment and purity of the more readily adsorbed
component into the heavy product, or higher yield (recovery) of the
less readily adsorbed component into the light product. This
apparatus may also be configured to deliver the heavy product at
elevated pressure, here approximately the higher working pressure
so that both product gases are delivered at about the higher
pressure.
[0109] The apparatus of FIG. 12 has infeed conduit 300 to introduce
the feed gas at substantially the higher pressure to first feed
manifold 53. As in the example of FIG. 11, adsorber pressurization
is achieved mainly by light reflux, with a final feed
pressurization step through manifold 53.
[0110] A multistage heavy reflux compressor 301 has a first stage
302 as third exhaust means 184 of FIG. 7, drawing heavy gas by
conduit 246 from first product exhaust manifold 61, and compressing
this gas through intercooler 303 to second stage 304. Heavy reflux
compressor second stage 304 as second exhaust means 183 also draws
heavy gas from second countercurrent blowdown manifold 59 through
conduit 244, and delivers this gas by intercooler 305 to third
stage 306 which as first exhaust means 181 also draws heavy gas
from first countercurrent blowdown manifold 57 through conduit 240,
and delivers this gas by intercooler 307 to fourth stage 308 which
attains substantially the higher working pressure of the PSA cycle.
The heavy reflux compressor is driven by prime mover 209 through
shaft 210, and by light reflux expander 220 through shaft 309.
[0111] The compressed heavy gas is conveyed from compressor fourth
stage 308 by conduit 310 to condensate separator 311, from which
the heavy product is delivered by conduit 312 which is externally
maintained at substantially the higher pressure less frictional
pressure drops. Condensed vapours (such as water or liquid
hydrocarbons) are removed through conduit 313 at substantially the
same pressure as the heavy product in conduit 312. The remaining
heavy gas flow, after removal of the first product gas, flows by
conduit 314 to the second feed manifold 55 as heavy reflux to the
adsorbers following the feed step for each adsorber. The heavy
reflux gas is a second feed gas, of higher concentration in the
more readily adsorbed component or fraction than the first feed
gas.
[0112] FIG. 13
[0113] FIG. 13 shows a PSA apparatus with a free rotor tail gas
compressor or vacuum pump, powered by energy recovery expanders
analogous to a multistage turbocharger. Free rotor compressor 320
includes, on shaft 321, tail gas compressor 322 (or vacuum pump
322, if the lower pressure is subatmospheric) which is the third
exhaust means 184 drawing heavy product gas or tail gas from
exhaust manifold 61. In this example, the heavy product gas is
discharged from conduit 243 at the second countercurrent blowdown
pressure 182, which is above the lower pressure. Pressure 182 may
here be atmospheric pressure, in which case the third exhaust means
is a vacuum pump. Conduit 244 is the second exhaust means 183. The
first exhaust means 181 is expander 323 coupled to shaft 321 of
free rotor compressor 320. Expander 323 expands heavy gas flowing
from manifold 57 through conduit 240 and optional heater 241, and
releases that gas to exhaust conduit 243.
[0114] The light reflux expander 220 and the countercurrent
blowdown expander 323 are both coupled to drive the tail gas
compressor 322 by shaft 321, with no other source of mechanical
power required. The application of energy recovery (from light
reflux and countercurrent blowdown) provides the alternative
benefits of reducing the lower pressure so as to improve PSA (or
VPSA) cycle performance, or raising the first product delivery
pressure as may be required e.g. for tail gas disposal, without the
requirement for an electric motor driven compressor. This feature
would be particularly useful for hydrogen separation, where
reducing the lower pressure greatly improves performance, while
elevated tail gas pressures may be desired. Alternatively, a
hydrogen PSA system could be operated with a subatmospheric lower
pressure, while the tail gas is discharged at sufficiently above
atmospheric pressure for combustion in a flare or furnace.
[0115] FIG. 14
[0116] FIG. 14 shows another embodiment using a free rotor
compressor or turbocharger. In this embodiment, applied to oxygen
separation from air, a motor driven first feed compressor 330 is
driven by prime mover 209 through shaft 210. Using the same
nomenclature and reference numerals of feed compression stages as
FIG. 8, feed compressor 330 includes feed compression first stage
202 and third stage 206 on shaft 210 driven by motor 209. Free
rotor second compressor 340 includes feed compression second stage
204 and fourth stage 208 on shaft 222, driven by countercurrent
blowdown expander 221 and light reflux expander 220 through shaft
222. This configuration enables operation of a motor driven feed
compressor with a limited number of stages (here 2 stages) to
operate a PSA cycle with a larger number of feed supply pressures
(here the three pressures 161, 163 and 151 of FIG. 6), since the
free rotor compressor has dual functions as means to boost feed
pressure by application of thermally boosted expansion energy
recovery, and means to split the stage intermediate pressures for
supply to the PSA module.
[0117] FIG. 15
[0118] FIG. 15 shows a VPSA oxygen generation plant with 4 modules
in parallel, each having a free rotor booster compressor powered by
energy recovery expanders, and the entire apparatus having a single
prime mover 350 which may for example be an electric motor or a gas
turbine. Prime mover 350 drives first feed compressor 351 on shaft
352. Feed compressor 351 has a first stage 353 drawing feed gas
from infeed conduit 200, and a third stage 354. The second stage of
feed compression is provided by the free rotor compressors of each
module. The first feed compressor 351 in this embodiment also
includes an exhaust vacuum pump 355 likewise coupled to shaft
352.
[0119] The plant includes four identical modules 10A, 10B, 10C and
10D. In FIGS. 15 and 16, component nomenclature and reference
numerals follow that established for FIGS. 1-14, with a suffix A to
D appended to the reference numerals for module components, and
each component so identified with reference to any one module will
be identically found in each of the other modules. The first
manifolds are identified with reference to module 10D as 48D and
51D for feed pressurization, 53D for feed supply at the higher
pressure, 57D and 59D for countercurrent blowdown, and 61D for
exhaust at the lower pressure. The second manifolds are identified
with reference to module 10C as 71C communicating to light product
delivery manifold 360 and delivery conduit 218, light reflux exit
manifolds 73C, 75C, 77C and 79C, and light reflux return manifolds
81C, 83C, 85C and 87C.
[0120] The identical free rotor compressor for each module will be
described with reference to module 10B. Free rotor compressor
assembly 370B includes feed compression second stage 371B and
vacuum pump 372B, both coupled by shaft 373B to light reflux
expander 220B. Feed gas compressed by feed compressor first stage
353 is conveyed by feed manifold 376 in parallel to the first feed
pressurization manifold (e.g. 48D) of each module, and to the inlet
of feed compression second stage (e.g. 371B) of the free rotor
compressor assembly (e.g. 370B) of each module which delivers
further compressed feed pressurization gas to the second feed
pressurization manifold (e.g. 51D) of each module. Feed gas
compressed to the higher pressure by third feed compressor stage
354 is conveyed by feed manifold 377 in parallel to the first feed
supply manifold (e.g. 53D) of each of the modules. Heavy gas at the
lower pressure is drawn from the heavy compartment (e.g. 61D) of
each module through vacuum exhaust manifold 378 to exhaust vacuum
pump 355 as the third exhaust means. Countercurrent blowdown gas
from the first countercurrent blowdown manifold (e.g. 57D) of each
module is discharged by e.g. conduit 240B as first exhaust means,
while countercurrent blowdown gas from the second countercurrent
blowdown manifold (e.g. 59D) of each module is exhausted by vacuum
pump (e.g. 372B) of the free rotor compressor assembly as second
exhaust means, delivering the heavy tail gas to the module heavy
product or waste gas exhaust, e.g. 243B.
[0121] FIG. 16
[0122] FIG. 16 shows a PSA apparatus with 5 modules 10A-10E. In
this embodiment, the prime mover, all compressor stages and all
expander stages are directly mechanically coupled (e.g. on a single
shaft) following the embodiment and component descriptions of FIG.
8, with the only difference being the connection in parallel of
multiple modules.
[0123] FIG. 17
[0124] In this example, sealing faces 21 and 23 are respectively
provided as hard-faced ported surfaces on the first and second
valve stators 40 and 41. Sliding seals 380 are provided on rotor 11
between each adsorber 24 and its neighbours, to engage both sealing
faces 21and 23 in fluid sealing contact. Seals 380 may have a wear
surface of a suitable composite material based on PTTE or carbon,
and should be compliantly mounted on rotor 11 so as to compensate
for wear, deflections and misalignment. Ports 381 may be sized,
particularly at the leading edge of each compartment, to provide
controlled throttling for smooth pressure equalization between
adsorbers and that compartment, as each adsorber in turn is opened
to that compartment.
[0125] Split stream vacuum pump 260 receives the countercurrent
blowdown and exhaust flow in three streams receiving exhaust gas at
incrementally reduced pressures from countercurrent blowdown
compartment 56, compartment 58 and compartment 60. The combined
exhaust gas is discharged as heavy product gas. In this example,
initial feed pressurization is performed from atmosphere, so a
first feed pressurization conduit 382 admits feed air directly from
inlet filter 200 to first feed pressurization compartment 46 at
substantially atmospheric pressure. The first discharge port of
feed compressor 201 now communicates to second feed pressurization
compartment 50. The compressor is shown as a split stage machine
with inlet 391, and three discharges 392, 393 and 394 at
incrementally higher pressures.
[0126] In the option of light reflux pressure letdown with energy
recovery, a split stream light reflux expander 220 is provided to
provide pressure let-down of four light reflux stages with energy
recovery. The light reflux expander provides pressure let-down for
each of four light reflux stages as illustrated. As indicated by
dashed lines 395, the stages may optionally be compartmentalized
within the light reflux expander to minimize mixing of gas
concentration between the stages. The light product purity will
tend to decline from the light reflux stages of higher pressure to
those of lower pressure, so that a desirable stratification of the
light reflux can be maintained if mixing is avoided.
[0127] Light reflux expander 220 is coupled to drive light product
pressure booster compressor 396 by shaft 397. Compressor 396
receives the light product from compartment 70, and delivers light
product (compressed to a delivery pressure above the higher
pressure of the PSA cycle) from delivery conduit 218. Since the
light reflux and light product are both enriched oxygen streams of
approximately the same purity, expander 220 and light product
compressor 396 may be hermetically enclosed in a single housing
similar to a turbocharger.
[0128] FIG. 18
[0129] FIG. 18 shows a radial flow rotary PSA module 500,
contemplated for tonnage oxygen generation. With reference to FIG.
17, this view may be interpreted as an axial section through
compartments 54 and 70 at the higher pressure, and compartments 80
and 60 at the lower pressure. Arrows 501 and 502 respectively
indicate the feed and exhaust flows. Rotor 11 has a first end plate
510 with stub shaft 511 supported by bearing 512 in first bearing
housing 513, which is integral with first valve stator 40. Rotor 11
is attached at assembly joint 514 to a second end plate 515 with
stub shaft 516 supported by bearing 517 in second bearing housing
518, which is attached at assembly joint 519 to first valve stator
40.
[0130] Rotor 11 is driven by motor 95 connected to stub shaft 511
by shaft 94 penetrating housing 513 through shaft seal 522. First
end plate 510 has no perforations that might compromise purity of
the light product gas by leakage from the first valve surface to
the second valve surface. Second end plate 515 is penetrated at
bushing 530 by the second valve stator. Second valve stator 41 is a
stationary pintle within rotor 11, with guide bushings 530 and 532,
and is attached to the second bearing housing 518 at assembly face
534. Bearings 512 and 517 may be much smaller in diameter than the
outer diameter of rotor 11 at sealing face 21. A shaft seal 535 is
provided between shaft 516 and bearing 517, to prevent
contamination of the light product gas by leakage from chamber 536
adjacent the first valve sealing face 21 to chamber 537 adjacent
the second valve sealing face 23.
[0131] Preferably, seal 535 is tight against leakage so that
product purity is not compromised. By configuring this seal at
smaller diameter than the valve sealing faces, frictional torque
from shaft seal 535 is greatly reduced than if this seal were at
the full rotor diameter. Leakage across seals in the first valve
face is much less important, because moderate leakage across those
seals simply reduced the volumetric efficiency of the process.
Similarly, moderate leakage across the seals in the second valve
face may be tolerated, as the concentration of light reflux gases
and the light product gas that may leak across those seals is
almost identical. Because moderate leakage across seals in the
first valve surface (including circumferential seals 96), and
across seals in the second valve surface (including circumferential
seals 97), can be accepted, all of those seals may be designed for
relatively light mechanical engagement to minimize frictional
torque. In fact, use of narrow gap clearance seals or labyrinth
seals with zero mechanical rubbing friction is an attractive option
especially for larger capacity modules operating at high cycle
frequency (e.g. 50 or 100 cycles per minute) where seal leakage
flows would have a minimal effect on overall efficiency.
Preferably, the seals in the first and second valve faces have
consistent performance and leakage, so that all "N" adsorbers
experience the same PSA cycle flow and pressure regime as closely
as possible, without being upset by variations in leakage between
the adsorbers.
[0132] Hence an important benefit of the present invention is that
close tolerance sealing is only required on one dynamic rotary
seal, shaft seal 535, whose diameter has been made much smaller
than the rotor diameter to reduce the sealing perimeter as well as
mechanical friction power loss. For a given rotary seal section and
loading, rubbing friction power loss at given RPM is proportional
to the square of the sealing face diameter.
[0133] Because of the compactness (similar to an automotive
turbocharger) of a "turbocompressor" oxygen booster as described
for FIG. 17above, it is possible to install a split stream light
reflux expander 220 with close-coupled light product compressor 396
inside the light valve stator. Compressed oxygen product is
delivered by conduit 218.
[0134] FIG. 19
[0135] FIG. 19 shows an axial flow rotary PSA module 600 for
smaller scale oxygen generation. The flow path in adsorbers 24 is
now parallel to axis 601. A better understanding will be obtained
from FIGS. 20, 21 and 22, which are cross sections of module 600 in
the planes respectively defined by arrows 602-603, 604-605, and
606-607. FIG. 19 is an axial section of module 600 through
compartments 54 and 70 at the higher pressure, and compartments 60
and 80 at the lower pressure. The adsorber rotor 11 contains the
"N" adsorbers 24 in adsorber wheel 608, and revolves between the
first valve stator 40 and the second valve stator 41. Compressed
feed air is supplied to compartment 54 as indicated by arrow 501,
while nitrogen enriched exhaust gas is exhausted from compartment
60 as indicated by arrow 502.
[0136] At the ends of rotor 11, circumferential seals 608 and 609
bound first sealing face 21, and circumferential seals 610 and 611
bound second sealing face 23. The sealing faces are flat discs. The
circumferential seals also define the ends of seals between the
adsorbers, or alternatively of dynamic seals in the sealing faces
between the stator compartments. Rotor 11 has a stub shaft 511
supported by bearing 512 in first bearing housing 513, which is
integral with first valve stator 40. Second valve stator 41 has a
stub shaft engaging the rotor 11 with guide bushing 612.
[0137] A flanged cover plate 615 is provided for structural
connection and fluid sealing enclosure between the first valve
stator 40 and the second valve stator 41. Rotor 11 includes seal
carrier 618 attached at joint 619 to adsorber wheel 608, and
extending between the back of second valve stator 41 and cover
plate 615 to sealing face 621 which is contacted by dynamic seal
625. Seal 625 prevents contamination of the light product gas by
leakage from chamber 626 adjacent the first valve sealing face 21
to chamber 627 adjacent the second valve sealing face 23.
[0138] Seal 625 needs to be tight against leakage that could
compromise product purity. By this seal to a smaller diameter than
the valve faces outer diameter, frictional torque from this seal is
greatly reduced than if this seal were at the full rotor diameter.
The circumferential perimeter exposed to leakage is also reduced.
As in FIG. 18, the light reflux pressure letdown means, illustrated
as a split stream light reflux expander 220 with close-coupled
light product compressor 396, may be installed inside the light
valve stator.
[0139] FIG. 20
[0140] FIG. 20 shows an axial flow rotary PSA module 650 with twin
adsorber wheels. The same reference numerals are used as in FIG. 19
for the first adsorber wheel 608, and primed reference numerals are
used for the second adsorber wheel 608', which are assembled
together as rotor 11. Module 650 has two first valve faces 21 and
21', each with a full set of feed supply and second product exhaust
compartments. External manifolds will be provided to supply feed
fluid to each pair of feed compartments and to withdraw exhaust
fluid from each pair of exhaust compartments. Module 650 has two
second valve faces 23 and 219', which share a common set of
compartments for light product delivery, light reflux exit and
return, and purge. Arrows 651 indicate the flow direction in
compartment 221, and arrows 652 indicate the flow direction in
compartment 70.
[0141] Rotor 11 is driven by shaft 94 coupled to the first adsorber
wheel 608. The adsorber wheels 408 and 608' are attached at joint
655. Flanged cover plate 615 of FIG. 19 is here replaced by the
first valve stator 40' for the second adsorber wheel 608', in the
role of connecting the first valve stator 40 and second valve
stator 41 to form an enclosed housing for the module. A small
diameter dynamic seal 660 is mounted adjacent bushing 612', to
prevent leakage between the first and second valve faces.
[0142] Embodiment 650 enables a doubled capacity rating for the
twin axial wheel configuration compared to the single wheel
embodiment 600.
[0143] FIG. 21
[0144] FIG. 21 shows the first valve face 21 of embodiment 600 of
FIG. 19, at section 602-603, with fluid connections to a split
stream feed compressor 201 and a split stream countercurrent
blowdown expander 221. Arrow 670 indicates the direction of
rotation by adsorber rotor 11. The open area of valve face 21
ported to the feed and exhaust compartments is indicated by clear
angular segments 46, 50, 52, 56, 58, 60 corresponding to those
compartments, between circumferential seals 608 and 609. The closed
area of valve face 21 between compartments is indicated by
cross-hatched sectors 675 and 676. Typical closed sector 675
provides a transition for an adsorber, between being open to
compartment 56 and open to compartment 58. Gradual opening is
provided at the leading edges 677 and 678 of compartments, so as to
achieve gentle pressure equalization of an adsorber being opened to
a new compartment. Much wider closed sectors (e.g. 676) are
provided to substantially close flow to or from one end of the
adsorbers when pressurization or blowdown is being performed from
the other end.
[0145] Sealing between compartments at typical closed sectors (e.g.
675) may be provided by rubbing seals on either stator or rotor
against a ported hard-faced sealing counter face on the opposing
rotor or stator, or by narrow gap clearance seals on the stator
with the area of the narrow sealing gap defined by the cross
hatched area of the nominally closed surface. Rubbing seals may be
provided as radial strip seals, with a self-lubricating solid
material such as suitable PTFE compounds or graphite, or as brush
seals in which a tightly packed brush of compliant fibers rubs
against the counter face.
[0146] If the rubbing seals are on the rotor (between adjacent
adsorbers), cross-hatched sectors 675 and 676 would be non-ported
portions of the hard-faced sealing counter face on the stator. If
the rubbing seals are on the stator, the ported hard-faced counter
face is on the rotor valve face. Those rubbing seals could be
provided as full sector strips for narrow closed sectors (e.g.
675). For the wider closed sectors (e.g. 676), narrow radial
rubbing seals may be used as the edges 678 and 679, and at
intervals between those edges, to reduce friction in comparison
with rubbing engagement across the full area of such wide
sectors.
[0147] Clearance seals are attractive, especially for larger scale
modules with a very large number "N" of adsorbers in parallel. The
leakage discharge coefficient to or from the clearance gap varies
according to the angular position of the adsorber, thus providing
gentle pressure equalization as desired. The clearance gap geometry
is optimized in typical nominally closed sectors (e.g. 675) so that
the leakage in the clearance gap is mostly used for adsorber
pressure equalization, thus minimizing through leakage between
compartments. The clearance gap may be tapered in such sectors 675
to widen the gap toward compartments being opened, so that the rate
of pressure change in pressure equalization is close to linear. For
wide closed sectors (e.g. 676) the clearance gap would be
relatively narrow as desired to minimize flows at that end of
adsorbers passing through those sectors.
[0148] For all types of valve face seals described above, it is
preferable that consistent performance be achieved over time, and
that all "N" adsorbers experience the same flow pattern after all
perturbations from seal imperfections. This consideration favours
placing rubbing seals on the stator so that any imperfections are
experienced similarly by all adsorbers. If the seals are mounted on
the rotor between adsorbers, it is preferable that they are closely
identical and highly reliable to avoid upsetting leakages between
adjacent adsorbers.
[0149] To compensate for misalignment, thermal distortion,
structural deflections and wear of seals and bearings, the sealing
system should have a suitable self-aligning suspension. Thus,
rubbing seal or clearance seal elements may be supported on
elastomeric supports, bellows or diaphragms to provide the
self-aligning suspension with static sealing behind the dynamic
seal elements. Rubbing seals may be energized into sealing contact
by a combination of elastic preload and gas pressure loading.
[0150] Clearance seals require extremely accurate gap control,
which may be established by rubbing guides. Clearance seal gap
control may also be achieved by a passive suspension in which the
correct gap is maintained by a balance between gas pressure in the
gap of a clearance seal segment, and the pressures of adjacent
compartments loading the suspension behind that segment. For seal
elements between blowdown compartments, a simple passive
self-adjusting suspension should be stable. Active control elements
could also be used to adjust the clearance seal gap, with feedback
from direct gap height measurement or from the pressure gradient in
the gap. Active control may be considered for seal elements between
pressurization compartments, for which the simple passive control
may be unstable.
[0151] FIG. 22
[0152] FIG. 22 shows the second valve face 23 of embodiment 600 of
FIG. 19, at section 604-605, with fluid connections to a split
stream light reflux expander 220 and light product booster
compressor 396. Fluid sealing principles and alternatives are
similar to those of FIG. 21. Similar principles and alternatives
apply to radial flow and axial flow geometries, respectively
sealing on cylindrical or disc faces.
[0153] FIG. 23
[0154] Adsorber wheel 608 may use radially aligned rectangular flat
packs of adsorbent laminate, as shown in FIG. 5 for radial flow.
FIG. 23 shows an alternative adsorber wheel configuration for the
embodiment of FIG. 19, at section 606-607. As in FIG. 5, the
adsorbers 24 are again formed of a pack of rectangular adsorbent
sheets with spacers, but with the sheets here curved arcs rather
than flat. With this configuration, the ports and seals in valve
faces 21 and 23 would desirably be configured as corresponding
curved arcs. Voids between the circularly curved adsorber packs are
filled by separators 684. Such circularly curved adsorber packs may
be made by forming the adsorbent sheets with spacers in a spiral
roll on a circular cylindrical mandrel, and then cutting the spiral
roll longitudinally to obtain the desired packs. Packing density
may be further improved by forming the adsorber sheets to a spiral
rather than circular curve.
[0155] FIGS. 24-27
[0156] FIG. 24 shows a multistage centrifugal compressor 400 with
impulse turbine expanders for the light reflux and countercurrent
blowdown, configured to provide the feed compressor stages 202,
204, 206 and 208, the countercurrent blowdown expander stages 242
and 245, and the light reflux expander stages 226, 230, 234, and
238 of FIG. 8. Prime mover 209 drives shaft 402, supported in
compressor casing 403 by bearings 404 and 405 on axis 406. Shaft
402 carries compressor first stage impeller 411, second stage
impeller 412, third stage impeller 413 and fourth stage impeller
414, exhaust impulse turbine runner 415 and light reflux impulse
turbine runner 416.
[0157] Feed air from PSA plant inlet 200 enters suction port 420 to
suction scroll 421 to the inlet 422 of impeller 411. Impeller 411
discharges the air to first stage diffuser 425 and first stage
collector scroll 426, which directs the first stage compressed air
to the inlet of the second stage impeller 412. Impeller 412
discharges the air to second stage diffuser 430 and second stage
collector scroll 431, from which second stage delivery port 432
discharges a portion of the feed air as pressurization gas at the
second stage pressure to conduit 212. Similarly, the feed air is
compressed by the third and fourth stage impellers 413 and 414,
discharging air at the third stage pressure from third stage
delivery port 436 communicating to conduit 214, and at the fourth
stage pressure from fourth stage delivery port 440.
[0158] The multistage centrifugal compressor 400 provides the
stages of feed compressor 201 in FIG. 8. Multistage vacuum pumps,
as required in the embodiment of FIG. 9, may similarly be provided
as conventional centrifugal stages. For a large multiple module
plant, for example as described in FIG. 16, the exhaust and light
reflux expander turbines may be provided as multistage radial
inflow turbines whose stages would be mechanically similar to the
centrifugal stages of FIG. 24. In larger plants, expander stages
may also be provided as full admission axial turbine stages,
similar to gas turbine stages.
[0159] For particular advantage in smaller plant capacities,
considerable simplification is obtained in the embodiment of FIGS.
24-27 by using partial admission impulse turbines for
countercurrent blowdown and light reflux expansion, with each
expander stage occupying a sectoral arc of the corresponding
turbine on a single runner wheel. This approach is practicable
because the stages for each turbine expand gases of approximately
similar composition across adjacent pressure intervals.
[0160] FIG. 25 is a section of FIG. 24, defined by arrows 451 and
452, across the plane of light reflux impulse turbine runner 416.
FIG. 24 is a section of FIG. 25, in the plane indicated by arrows
453 and 454. Runner 416 rotates about axis 406 in the direction
indicated by arrow 455. Runner 416 has blades 456 mounted on its
rim. FIG. 26 is a projected view of the light reflux expander
impulse turbine, unrolled around 360.degree. of the perimeter of
the impulse turbine as indicated by the broken circle 458 with ends
459 and 460 in FIG. 25.
[0161] The light reflux turbine has four nozzles serving the four
90.degree. quadrants of the runner to provide the four expansion
stages, including first nozzle 461 receiving flow from port 462
communicating to conduit 224, second nozzle 463 receiving flow from
port 464 communicating to conduit 228, third nozzle 465 receiving
flow from port 466 communicating to conduit 232, and fourth nozzle
467 receiving flow from port 468 communicating to conduit 236.
[0162] The first stage light reflux flow from nozzle 461 impinges
blades 456, and is collected in diff-user 471 and discharged at the
reduced pressure by port 472 communicating to conduit 227.
Similarly the light reflux flow from nozzle 463 is collected in
diff-user 473 and flows by port 474 to conduit 231, the light
reflux flow from nozzle 465 is collected in diffuser 475 and flows
by port 476 to conduit 235, and the light reflux flow from nozzle
467 is collected in diffuser 477 and flows by port 478 to conduit
239. To minimize interstage leakage losses, the channel gap 479
between the casing 403 and blades 456 of runner 416 is
appropriately narrow between quadrants.
[0163] The exhaust expander turbine, or countercurrent blowdown
expander turbine, has two stages. Its sectional arrangement is
similar to that depicted in FIG. 25, except that two rather than
four nozzles and diffusers are required for the two exhaust stages.
FIG. 27 is an unrolled projection around exhaust turbine runner 415
as indicated by broken circle 458 for the light reflux turbine. The
exhaust turbine has impulse blades 480 on runner 415. Nozzle 481
receives the first countercurrent blowdown stream by port 482
communicating to conduit 240, while nozzle 483 receives the second
countercurrent blowdown stream by port 484 communicating to conduit
244. Nozzles 481 and 483 have guide vanes 485 and 486, and direct
the countercurrent blowdown flows to impinge on blades 480 in
opposite half sectors of the turbine 415. After deflection by
blades 480, the expanded flow from nozzle 481 is collected in
diffuser 491, and is passed to collector ring manifold 492. The
flow from nozzle 483 likewise passes the blades 480 and is
collected in diffuser 493 joining manifold 492 to deliver the
combined low pressure exhaust flow by exhaust port 494 which is
connected to the discharge 243.
[0164] FIG. 28
[0165] FIG. 28 shows a three stage axial flow split stream
compressor 700. While it is known in the prior art to divert minor
bleed flows between stages of multistage axial flow compressors or
expanders, compressor 700 has nested annular diffusers for
splitting fractionally large intermediate flows from the main flow
between stages.
[0166] Compressor 700 may represent split stream compressor 201 of
FIG. 4, and has a scroll housing 701 with feed inlet 391, first
discharge port 392, second discharge port 393 and third discharge
port 394. Rotor 702 is supported by bearings 703 and 704 with shaft
seals 705 and 706 within housing 701, and is driven by motor 209
through shaft 210. The rotor supports first stage rotor blades 711,
second stage rotor blades 712, and third stage rotor blades
713.
[0167] Housing 701 includes an inlet scroll 721 distributing feed
gas from inlet 391 to annular feed plenum 722, with the flow
direction indicated by arrow 723. The feed flow enthalpy is
increased by first stage blades 711, with static pressure recovery
by first stage stator blades 724 mounted in first stage stator ring
725. The feed flow enthalpy is further increased by second stage
blades 712, with static pressure recovery by second stage stator
blades 726 mounted in second stage stator ring 727; and finally by
third stage blades 713, with static pressure recovery by third
stage stator blades 728 mounted in third stage stator ring 729.
[0168] Second stage stator ring 727 has a smaller diameter than
first stage stator ring 725, defining an annular area of annular
first stage diffuser 731 which delivers the first intermediate feed
pressurization flow to collector scroll 732 and thence to first
discharge port 392 as indicated by arrow 733. Similarly, third
stage stator ring 729 has a smaller diameter than second stage
stator ring 727, defining an annular area of annular second stage
diffuser 734 which delivers the first intermediate feed
pressurization flow to collector scroll 735 and thence to second
discharge port 393 as indicated by arrow 736. The fraction of flow
entering the first and second stage annular diffusers is
substantially equal to the ratio of the annular area of those
diffuser inlets to the annular flow area of that stage between its
stator ring and the rotor 702.
[0169] The flow delivered by the third stage passes stator blades
728 into third stage diffuser 737, and in collector scroll 738 into
discharge port 394 as indicated by arrow 739. Stator rings 725, 727
and 729 are respectively supported by partitions 741, 742 and 743
separating the inlet and discharge scrolls.
[0170] It will be evident that additional stages could be added
with more paired sets of rotor blades and stator blades, with the
option of including or not including an annular diffuser for
diverting an intermediate flow stream between any adjacent pair of
stages. It will also be evident that the structure of compressor
700 could be applied to a split stream axial flow vacuum exhauster
or expander, by reversing the flow directions indicated by arrows
723, 733, 736, and 739, so that port 394 would be a first inlet,
port 393 a second inlet, and port 392 a third inlet for each of
three inlet streams at incremental total pressures, and with port
391 the discharge port for the combined total flow.
[0171] FIG. 29
[0172] FIG. 29 shows a composite adsorbent pellet 800, useful in
the practice of the present invention with the radial flow
configuration of FIGS. 4, 5, 6 and 18, in the alternative of using
granular packed bed adsorbers 24.
[0173] Granular adsorbent beds cannot be operated in prior art PSA
devices at very high cycle frequency without excessive pressure
drops leading to incipient fluidization and resulting attrition.
The present apparatus in the radial flow configuration provides a
centripetal acceleration field which may be greater than the
ordinary gravitational field. This provides a desirable
"centrifugal clamping" effect to stabilize the adsorbent bed, and
thus facilitate safe operation at higher cycle frequency. However,
the specific gravity of conventional macroporous zeolite adsorbent
pellets is only about 0.75, thus limiting the effect of centrifugal
clamping. While the use of rotating granular adsorbent beds in
radial flow configurations is well known in the above cited prior
art, operating conditions that would provide useful centrifugal
clamping have not been disclosed. Thus, Boudet et al in U.S. Pat.
No. 5,133,784 contemplate a maximum cycle frequency and rotor speed
of 20 RPM, which with their mentioned rotor outer radius of 1 meter
would provide a maximum centripetal acceleration of less than half
the acceleration of gravity at the outer radius. The adsorbent
beds, within the rotor and closer to the axis, are subject to a
much smaller centripetal acceleration.
[0174] Ballasted composite pellet 800 has an inert core 801 of a
dense material, surrounded by a coating 802 of macroporous zeolite
material similar to the material of conventional adsorbent pellets.
The core material may be selected for high density, high heat
capacity, high thermal conductivity and compatibility for adhesion
to zeolite binders as well as for thermal expansion. Suitable core
materials include transition metal oxides, most simply iron oxide,
as well as solid iron or nickel-iron alloys.
[0175] If the diameter of core 801 is e.g. 790 microns, and the
radial thickness of coating 802 is e.g. 105 microns so that the
overall diameter of a spherical pellet 800 is 1 mm, the volume of
the pellet is then 50% inert and 50% active macroporous adsorbent.
In a packed bed using such composite pellets, the active volume of
adsorbent has been reduced by 50%, while the fractional bed voidage
of the active material has been increased from the typical 35% of
spherical granular media to approximately 50%. This might seem to
be an inferior packed bed, with half as much useful material and
reduced effective selectivity performance because of the high
effective void fraction. Unexpectedly, this can be a superior
packed bed, because pressure drop and mass transfer resistance are
both reduced, so that the PSA cycle can be operated at higher cycle
frequency without excessive pressure drop and without risk of
fluidization. At the same cycle frequency, pressure drops are
reduced by the smaller flows in proportion to the smaller active
adsorbent inventory for the same voidage channels, while mass
transfer through the macropores only has to take place through a
relatively thin shell. The inert material also acts as thermal
ballast to isothermalize the adsorber against thermal swings due to
heat of adsorption.
[0176] While the higher void fraction will reduce product yield at
specified purity in the uneconomic regime of very low cycle
frequency, product yield and productivity are actually enhanced in
the economic regime of higher cycle frequency. Degradations of
product yield and process energy efficiency (at specified product
purity) will result from mass transfer resistance and pressure
drop, and those degradations are more severe for the conventional
bed than for the present inventive granular adsorber of composite
pellets.
[0177] Such composite pellets are very useful in the radial flow
embodiment of the rotary adsorber module, since the heavy composite
pellets are centrifugally stabilized very positively, even as mass
transfer resistance and pressure drop are reduced. Such composite
pellets will also be very useful in axial flow embodiments, as well
as non-rotary adsorbers, with vertically oriented flow path. Again,
cycle frequency can be increased, while performance can be enhanced
in terms of productivity, yield and efficiency at the most economic
operating point. Consider FIGS. 4 and 18 to be vertical views of
radial flow embodiments. The vertical axis embodiment of FIG. 4
will benefit from centrifugal stabilization if its rotor radius and
cycle frequency are high enough. The horizontal axis embodiment of
FIG. 18 will have centripetal acceleration assisting the
gravitational field to suppress fluidization in the feed production
step with upward flow from compartment 54 to compartment 70 at
higher pressure, while the centripetal acceleration will assist
pressure drop in the purge step with upward flow from compartment
80 to compartment 60 at lower pressure to prevent downward collapse
of the adsorbers at the top of their rotational orbit. The
adsorbent beds are supported at their first end (radially outside)
by a first set of screens, and retained against collapsing when the
rotor is stopped by a second set of screens at their second end
(radially inside). Hence, the adsorbent beds are centrifugally
clamped on the first screens by centripetal acceleration with the
rotor acting as a centrifuge.
[0178] While composite pellets 800 are shown in FIG. 29 as
spherical, other geometries are also attractive. For example,
cylindrical composite pellets might be made by dip-coating the
zeolite and binder slurry onto steel rods, which are then cut into
short lengths.
[0179] The centrifugal clamping aspect of the present invention
allows operation of granular adsorbent beds with much higher than
conventional flow friction pressure gradients while still
positively preventing any particle movement and attrition. In turn,
this allows use of smaller adsorbent grain sizes, also enabling a
very shallow radial bed depth which reduces total pressure drop.
With the small adsorbent granule size reducing the mass transfer
diffusional resistance, high PSA cycle frequencies become
practicable. Closing the logical argument, high cycle frequencies
correspond to the high rotational speed needed for centrifugal
clamping.
[0180] The foregoing description of the preferred embodiments of
the invention is intended to be illustrative of the present
invention. Those of ordinary skill will be able to make certain
additions, deletions or modifications to the described embodiments
without departing from the spirit or scope of the invention as
defined by the appended claims.
* * * * *