U.S. patent number 3,848,430 [Application Number 05/397,090] was granted by the patent office on 1974-11-19 for absorption refrigeration machine with second stage generator.
This patent grant is currently assigned to The Trane Company. Invention is credited to Kenneth W. Gilster, Carl V. Loweth, James M. Porter.
United States Patent |
3,848,430 |
Porter , et al. |
November 19, 1974 |
ABSORPTION REFRIGERATION MACHINE WITH SECOND STAGE GENERATOR
Abstract
An absorption refrigeration machine having a second stage
generator which utilizes heat from the first stage generator high
pressure steam condensate and heat from the vapor generated in the
first stage to heat intermediate strength absorbent solution in the
second stage generator wherein expansion relieving means are
provided in said second stage generator.
Inventors: |
Porter; James M. (La Crosse,
WI), Loweth; Carl V. (La Crosse, WI), Gilster; Kenneth
W. (Onalaska, WI) |
Assignee: |
The Trane Company (La Crosse,
WI)
|
Family
ID: |
23569800 |
Appl.
No.: |
05/397,090 |
Filed: |
September 13, 1973 |
Current U.S.
Class: |
62/476; 62/497;
165/162; 165/82 |
Current CPC
Class: |
F25B
15/008 (20130101); Y02A 30/27 (20180101); Y02B
30/62 (20130101); Y02A 30/277 (20180101) |
Current International
Class: |
F25B
15/00 (20060101); F25b 015/06 () |
Field of
Search: |
;62/476,497
;165/82,162,81 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: O'Dea; William F.
Assistant Examiner: Ferguson; Peter D.
Claims
Therefore, what is claimed is:
1. In a two stage absorption refrigeration machine wherein the
second stage generator is heated by water vapor generated in the
first stage generator and water condensate formed in the first
stage generator from heating steam supplied through a steam control
valve, a second stage generator comprising: a shell defining an
enclosure; first conduit means for passing an absorption solution
from said first stage generator into said enclosure; a first
elongated tube bundle extending through said enclosure; a second
elongated tube bundle extending through said enclosure; second
conduit means for passing water vapor that is generated in said
first stage generator through the tubes of said first tube bundle;
third conduit means for passing steam condensate that is formed in
said first stage generator through the tubes of said second tube
bundle; each of said tube bundles being fixedly supported at their
ends by said shell; and means intermediate the ends of said second
tube bundle to accommodate longitudinal expansion of the tubes of
said second tube bundle relative to the tubes of said first tube
bundle during idle and start up conditions of said refrigeration
machine.
2. In a two stage absorption refrigeraton machine wherein the
second stage generator is heated by water vapor generated in the
first stage generator and water condensate formed in the first
stage generator from heating steam supplied through a steam control
valve, a second stage generator comprising: a shell defining an
enclosure; first condiut means for passing an absorption solution
from said first stage generator into said enclosure; a first
elongated tube bundle of first tubes extending through said
enclosure; a second elongated tube bundle of second tubes extending
through said enclosure; second conduit means for passing water
vapor that is generated in said first stage generator through said
first tubes of said first tube bundle; third conduit means for
passing steam condensate that is formed in said first stage
generator through said second tubes of said second tube bundle;
each of said tube bundles being supported by longitudinally spaced
alternately fixed and floating tube supports; at least some of said
floating tube supports of said second tube bundle being relatively
movable with respect to the floating tube supports of said first
tube bundle to permit longitudinal expansion of said second tubes
of said second tube bundle relative to said first tubes of said
first tube bundle during idle and start up conditions of said
refrigeration machine.
3. Apparatus as defined by claim 2 wherein the floating tube
supports of said second tube bundle are disposed substantially
longitudinally coextensive along said first and second tubes with
the floating tube supports of said first tube bundle.
4. Apparatus as defined by claim 3 including guide means connected
to the upper portions of longitudinally coextensive floating tube
supports to maintain the upper portions of said floating tube
supports in said longitudinally coextensive relationship.
5. Apparatus as defined by claim 3 wherein said guide means
includes protruding member carried by one of said floating tube
supports of one of said tube bundles and a socket member carried by
one of said floating tube supports of the other of said tube
bundles, said protruding member being slidably disposed in said
socket member for movement substantially normal to the longitudinal
axes of said first and second tubes for maintaining the associated
floating tube supports of each tube bundle in substantially
longitudinally coextensive relationship.
6. Apparatus of claim 5 wherein said first tubes and said second
tubes have a substantially straight natural configuration and said
fixed and floating tube supports are disposed intermediate the ends
of each of said tube bundles to constrain each of said tube bundles
into a wave-like configuration.
7. Apparatus of claim 6 including first limit means operatively
associated with each of said floating tube supports of said first
tube bundle for substantially limiting, at the respective floating
tube support substantial relative lateral movement between said
first tubes while permitting said first tubes to float as a group;
second limit means operatively associated with each of said
floating tube supports of said second tube bundle for substantially
limiting, at the respective floating tube support substantial
relative lateral movement between said second tubes while
permitting said second tubes to float as a group; and third limit
means operatively associated with each of said fixed tube supports
for substantially limiting at said fixed tube supports, relative
lateral movement between said first tubes, between said second
tubes, and between said first and second tubes, while permitting
said first and second tubes to pivot relative to the respective
fixed tube support.
8. Apparatus as defined by claim 7 including abutment means
associated with each of said floating tube supports of each of said
first and second tube bundles to permit each floating tube support
to move laterally substantially only to one side of its position
assumed when the tubes supported thereby are straight; said
abutment means permitting longitudinally spaced adjacent floating
tube supports to move substantially only to opposite sides and
longitudinally spaced alternate floating tube supports to move
substantially only to common sides.
9. Apparatus as defined in claim 8 wherein said abutment means are
located to permit said second tubes of said second tube bundle to
move from said natural straight configuration to said wave-like
configuration without said floating tube supports of said second
tube bundle interferring with the floating tube supports of said
first tube bundle.
10. Apparatus as defined by claim 9 wherein said abutment means are
located to permit longitudinally spaced alternate floating tube
supports of said first tube bundle, when in the wave-like
configuration, to occupy the space occupied by said floating tube
supports of said second tube bundle when the tubes thereof are in
their substantially straight natural configuration.
11. Apparatus as defined by claim 10 wherein longitudinally
coextensive fixed tube supports of each of said first and second
tube bundles are integral.
Description
BACKGROUND OF INVENTION
This invention relates to absorption refrigeration machines having
a two stage generator such as shown and described in U.S. Pat. No.
3,550,394. Further, this invention relates to a second stage
generator which employs expansion relieving means shown and
described in U.S. Pat. No. 3,212,570. More particularly this
invention relates to the discovery of and solution to certain
problems relating to second stage generator tube wear and
reliability.
An absorption refrigeration machine of the type shown in U.S. Pat.
No. 3,550,394 was built and operated. Design of the second stage
generator incorporated the principles of U.S. Pat. No. 3,212,570.
However, after some period of operation it was found that tubes
carrying steam condensate in the second stage generator would fail.
The reasons for these premature failures are not fully understood
nor were these failures anticipated because both the condensate and
the vapor carrying tubes of the second stage generator were
operated at nearly the same temperature. However, in retrospect it
is surmised that the steam condensate tubes were being heated at
some time to temperatures substantially higher than the vapor
conducting tubes. This could possibly occur in the event of leaking
of the high pressure steam control valve or could possibly be a
transient condition of start up.
SUMMARY OF THE INVENTION
This invention encompasses the discovery of certain problems and
the solution thereof relating to absorption refrigeration machines
employing second stage generators. More particularly, this
invention pertains to the discovery that tube failures of the
condensate tubes will occur despite tube expansion relieving means
unless further means are provided to permit longitudinal expansion
of condensate tubes relative to vapor tubes. The invention provides
means to allow the condensate tubes of the second stage generator
to expand longitudinally relative to the vapor tubes especially
where the condensate and vapor tubes are constrained to expanding
into a wave-like pattern upon elongation.
Specifically this invention involves a two-stage absorption machine
wherein the second stage generator is heated by water vapor
generated in the first stage generator and water condensate formed
in the first stage generator from heating steam supplied through a
steam control valve, a second stage generator comprising: a shell
defining an enclosure; first conduit means for passing an
absorption solution from said first stage generator into said
enclosure, a first elongated tube bundle of first tubes extending
through said enclosure; a second elongated tube bundle of second
tubes extending through said enclosure; second conduit means for
passing water vapor that is generated in said first stage generator
through said first tubes of first tube bundle; third conduit means
for passing steam condensate that is formed in said first stage
generator through said second tubes of said second tube bundle;
each of said tube bundles being supported by longitudinally spaced
alternately fixed and floating tube supports; at least some of said
floating tube supports of said second tube bundle being relatively
movable with respect to adjacent floating tube supports of said
first tube bundle to permit longitudinal expansion of said second
tubes of said tube bundle relative to said first tubes of said
first tube bundle during idle and start up conditions of said
refrigeration machine.
DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic of an absorption refrigeration machine having
a second stage generator incorporating the invention.
FIG. 2 is a horizontal section taken at line 2--2 of FIG. 1 showing
the second stage generator when the machine is turned completely
off.
FIG. 3 is a vertical section taken at line 3--3 of FIG. 2 showing a
fixed tube support.
FIG. 4 is a vertical section taken at line 4--4 of FIG. 2 showing a
floating tube support.
FIG. 5 is a vertical section taken at line 5--5 of FIG. 2 showing
another floating tube support.
FIG. 6 is a vertical section taken at line 6--6 of FIG. 5 showing a
detail of the floating tube support guide means.
FIG. 7 is a view similar to FIG. 2 showing the position of the two
tube bundles when heated during operation of the refrigeration
machine.
FIG. 8 is a vertical section taken at line 8--8 of FIG. 7.
FIG. 9 is a vertical section taken at line 9--9 of FIG. 7.
FIG. 10 is a view similar to FIG. 2 depicting what is thought to be
the appearance of the second stage generator during a transient
start up condition of the refrigeration machine or a condition
which may occur if valve 80 were to leak during periods when the
refrigeration machine is otherwise inactive.
FIG. 11 is a vertical section taken at line 11--11 of FIG. 10.
FIG. 12 is a vertical section taken at line 12--12 of FIG. 10.
DETAILED DESCRIPTION
Now with reference to FIG. 1 it will be seen that the absorption
machine has a fluid tight shell 10 enclosing a condenser 12, an
evaporator 14, an absorber 16, a first stage generator 18 and a
second stage generator 20. The refrigeration machine is supplied
with high pressure steam through a conduit 32 and cooling water,
such as from a cooling tower, through a conduit 24. Water such as
from a building to be chilled is conducted via a conduit to
evaporator heat exchanger 46 where such water is cooled and
returned via conduit 49 to meet the building cooling load.
For purposes of cooling, pump 48 circulates water via conduit 50
and spray nozzles 52 over heat exchanger 46 where upon a portion of
the water is evaporated to cool heat exchanger 46. The remaining
unevaporated water is returned via conduit 49 to pump 48 for
recirculation.
Water vapor thus formed in the evaporator is conducted to the
absorber 16 where it is absorbed in a solution of lithium bromide
and water pumped from pump 72 via conduit 76 to spray nozzles 78.
The heat which is generated during this absorption process is
removed from the absorber 16 via heat exchanger 22 supplied with
cooling water via conduit 24. The cooling water is discharged from
heat exchanger 22 via conduit 26 to condenser 12. A portion of the
dilute absorbent solution is removed from absorber 16 via conduit
74 to the inlet of pump 72 for admixture with concentrated
absorbent solution conducted through conduit 70 whereby an
intermediate strength absorbent solution is discharged from pump 72
through conduit 76. A second portion of dilute absorbent solution
is removed from absorber 16 via conduit 54 by pump 56. This portion
of dilute absorbent solution is discharged from pump 56 through
control valve 84, heat exchanger 58, heat exchanger 60, conduit 62,
to the first stage generator 18. Heat exchangers 58 and 60 serve to
preheat the dilute absorbent solution for improved efficiency.
In the first stage generator 18 the dilute absorbent solution is
heated by heat exchanger 34 and caused to boil. The water vapor
thus generated in the first stage generator is conducted from the
first stage generator via conduit 29 to vapor conducting heat
exchanger 38 of the second stage generator 20. The semiconcentrated
absorbent solution from first stage generator 18 is conducted via
conduit 64 through heat exchanger 60 and conduit 66 to second stage
generator 20. Heat exchanger 34 is supplied with high pressure
steam from a source such as a boiler via conduit 32 through steam
control valve 80. Steam condensate from heat exchanger 34 is
conducted through a steam trap 36 to steam condensate heat
exchanger 90 within the second stage generator 20. As an
alternative, not shown, the condensate leaving trap 36 may be heat
exchanged with the solution passing from heat exchanger 60 in
conduit 62 before passing to heat exchanger 90 for even greater
efficiency. Both valves 80 and 84 are controlled by a controller 82
responsive to load conditions as sensed by the temperature of the
chilled water leaving the evaporator at 83. The first stage
generator is enclosed by a shell or wall 35.
Partially concentrated absorbent solution entering the second stage
generator 20 from conduit 66 is heated by heat exchangers 38 and 90
and caused to boil. The water vapor thus generated in the second
stage generator 20 passes through a liquid eliminator 42 into
condenser 12 while the remaining concentrated absorbent solution is
conducted from the second stage generator via conduit 68, heat
exchanger 58, and conduit 70 to the inlet of pump 72 for admission
to the absorber via conduit 76 and spray nozzles 78 as aforeherein
described. The steam condensate passing in heat exchanger 90 is
returned to the steam source via conduit 91. The water vapor
passing in heat exchanger 38 is caused to condense and the
condensate is passed through condensate trap 40 to condenser 12 via
conduit 41. The second stage generator is enclosed by wall 43.
Condenser 12 is enclosed by pan or wall 29. A heat exchanger 28 is
arranged to conduct cooling water from conduit 26 to cool condenser
12, the cooling water being discharged from condenser 12 via
conduit 30 from which it may be returned to the cooling water
source such as a water cooling tower. The vapor passing through
liquid eliminators 42 and the refrigerant condensate passing from
conduit 41 are cooled by heat exchanger 28, the vapors being
thereby caused to condensed. The cooled and condensed refrigerant
passes from condenser 12 through an opening 44 in pan 29 to flow
directly into the evaporator 14.
It will be understood that shell 10 includes a tube sheet 51 at
each end thereof. Walls 35, 43, 29, 47 extend the full length of
shell 10 and are sealingly engaged with the tube sheets 51. The
tubes of heat exchangers 34, 38, 90, 28, 46, 22, extend into tube
sheets 51 at opposite ends. The inlets and outlets to these heat
exchangers while shown schematically in FIG. 1 are in actual
practice made by appropriate headers connected to the tube sheets
51.
Generator 20 is shown in more detail in FIGS. 2-12. Pan or wall 43
is in the form of a channel which as aforementioned extends between
tube sheets 51. Fixedly disposed within the channel are a plurality
of longitudinally spaced fixed tube supports 86. Each fixed tube
support is comprised of a vertical plate having a plurality of
apertures disposed in alignment with similar aperatures in tube
sheets 51 for receiving the bundle 87 of cupro-nickel tubes 88 of
heat exchanger 38 and the bundle 89 of cupro-nickel or stainless
steel tubes 91 of heat exchanger 90. The fixed tube support
aperatures are bored to a size of 0.003 to 0.010 inch larger than
the outer diameters of the tubes in the unheated condition to
accommodate thermaldiametrical expansion, bending and longitudinal
movement of the tubes therein. However, these apertures are
sufficiently small to prevent any substantial lateral movement of
the tubes therein. The tubes are of course expanded or otherwise
conventionally sealed within tube sheets 51.
Within channel or wall 43 between each pair of fixed tube supports
86 and between each tube sheet 51 and its most adjacent fixed tube
support 86 is a floating tube support 92 for supporting the tubes
88 of tube bundle 87 and the tubes 91 of tube bundle 89. The
floating tube supports are limited in longitudinal movement along
the channel 43 by stops or guide 93 in the form of angle members
welded to the base of channel member 43 as will be seen in FIG. 6.
The spacing of stops 93 on opposite sides of the floating tube
support 92 is normally such as to permit floating tube support 92
to move longitudinally a greater distance than the thickness of
floating tube support 92. Floating tube supports 92 are comprised
of metallic plates with through going holes to receive tubes 88 and
91. The holes in floating tube supports 92 are in the order of
0.003 to 0.010 so that the tubes are constrained against any
substantial lateral movement relative to the floating tube support
92 but may move laterally with the floating tube support 92.
Floating tube supports 92 may be divided into two groups, a first
set of alternate floating tube supports 94 and a second set of
alternate floating tube supports 95. Floating tube supports 94 are
constructed and supported so they can move laterally only to one
side of their position assumed when the tubes are in a straight
condition as shown in FIG. 2, that is when the heat exchangers 38
and 90 are at approximately room temperature. Floating tube
supports 95 are constructed and supported so that they can move
laterally only to the other side of their position assumed when the
tubes are in the aforesaid straight condition. By constructing and
supporting the floating tube supports in this manner the tubes will
assume a wave-like configuration upon being heated to operating
temperatures as will be seen more readily in FIG. 7.
Each floating tube support 94 is comprised of a major plate member
94a which traverses or encompasses the tubes 88 of tube bundle 87
and a minor plate member 94b which traverses or encompasses the
tubes 91 of tube bundle 89. Each plate member 94a is separate and
free to move relative to its associated plate member 94b. Adjacent
or associated plate members 94a and 94b are maintained in coplanar
relationship by an alignment means 96 hereinafter described. In
like manner each of floating tube supports 95 is comprised of a
major plate member 95a which traverses or encompasses the tubes 88
of tube bundle 87 and a minor plate member 95b which traverses or
encompasses the tubes 91 of tube bundle 89. Each of plate members
95b is separate and free to move relative to its associated plate
member 95a. Also adjacent or associated plate members 95a and 95b
are maintained in coplanar relationship by alignment means 96.
Each of alignment means 96 is comprised of a rod or protrusion 97
fixedly secured to a minor plate member and a socket member 98
fixedly secured to the major plate member for slidably receiving
rod 97. Such alignment means 96 is disposed both adjacent the top
and bottom of each of the floating tube supports.
It will be noted that major plate members 95a are constrained
against lateral movement to one side of their position shown in
FIG. 2 by reason of their abutment or contact at 99 with one wall
of channel member 43. Minor plate members 95b are similarly
constrained against lateral movement to one side of their position
shown in FIG. 2 by reason of their abutment or contact at 100 with
major plate members 95a. Minor plate members 94b are constrained
against lateral movement to the other side of their position shown
in FIG. 2 by reason of their abutment or contact at 101 with the
other wall of channel member 43. Each of major plate members 94a is
provided with a protrusion 102 fixedly secured thereto which abuts
said other wall of channel member 43 at 103 for constraining the
major plate member 94a against lateral movement to said other side
of its position shown in FIG. 2.
It will thus be seen that when tubes 91 of tube bundle 89 and tubes
88 of tube bundle 87 are heated to the same temperature and thereby
caused to elongate, they will assume the wave-like pattern
illustrated in FIG. 7. However, during start up conditions or
during idle periods when steam control valve 80 may leak thereby
permitting the tubes 91 of tube bundle 89 of heat exchanger 90 to
become heated while the tubes 88 of tube bundle 87 of heat
exchanger 38 remain relatively cool or at ambient temperature, the
tubes will assume the position shown in FIG. 10. Thus it will be
noted that the tubes of tube bundle 89 are free to move laterally
to a limited extent without interference from the tube bundle 87.
However, it does not follow that the tubes 88 of tube bundle 87 can
move laterally without interference with the tubes 91 of tube
bundle 89 by reason of the abuting relation of major plate members
95a and minor plate members 95b at 100. By reason of this same
relationship it will be seen that tube bundle 87 in moving from its
ambient temperature position shown in FIG. 2 to its heated position
shown in FIG. 7 actually occupies a portion of the space previously
occupied by tube bundle 89. By reason of this construction a more
compact double tube bundle construction is achieved. It will be
further noted that alignment means 96 are necessary to establish
the abutment at 100 and also serve to prevent the gouging of tubes
of one tube bundle by the floating tube support plate members of
the other tube bundle .
* * * * *