U.S. patent number 3,716,097 [Application Number 05/096,071] was granted by the patent office on 1973-02-13 for air condensation plant.
This patent grant is currently assigned to Kraftwerk Union Aktiengesellschaft. Invention is credited to Fritz Kelp, Hans-Heinrich Pohl.
United States Patent |
3,716,097 |
Kelp , et al. |
February 13, 1973 |
AIR CONDENSATION PLANT
Abstract
Air condensation plant for condensing steam by direct air
cooling includes mutually transversely disposed elongated cooling
elements traversible by steam along the length thereof, means for
directing a flow of air to a respective side of said cooling
elements, adjustable means for covering the side respectively of
the cooling elements for controlling the cooling thereof and for
preventing freezing, the cooling elements having an upper part
through which a preponderant quantity of the steam to be
condensated flows, the adjustable covering means being located in
front of the upper part of the cooling elements.
Inventors: |
Kelp; Fritz (Erlangen,
DT), Pohl; Hans-Heinrich (Erlangen, DT) |
Assignee: |
Kraftwerk Union
Aktiengesellschaft (Muhlheim (Ruhr), DT)
|
Family
ID: |
5753531 |
Appl.
No.: |
05/096,071 |
Filed: |
December 8, 1970 |
Foreign Application Priority Data
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Dec 11, 1969 [DT] |
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P 19 62 061.2 |
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Current U.S.
Class: |
165/299; 165/98;
165/101; 165/111; 165/126 |
Current CPC
Class: |
F28B
1/06 (20130101); F28B 9/005 (20130101); F01K
9/003 (20130101) |
Current International
Class: |
F28B
9/00 (20060101); F28B 1/00 (20060101); F01K
9/00 (20060101); F28B 1/06 (20060101); F28b
001/06 () |
Field of
Search: |
;165/39,111,122,126,98,99,101,103 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
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900,407 |
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Jul 1962 |
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GB |
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902,604 |
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Aug 1962 |
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GB |
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Primary Examiner: Davis, Jr.; Albert W.
Claims
We claim:
1. Air condensation plant for condensing steam by direct air
cooling which comprises mutually transversely disposed elongated
cooling elements traversible by steam along the length thereof,
means for directing a flow of air to a respective side of said
cooling elements, adjustable means for covering said side,
respectively, of said cooling elements for controlling the cooling
thereof and for preventing freezing, said cooling elements having
an upper part through which a preponderant quantity of the steam to
be condensed flows, said adjustable covering means compromising
flaps and being located in front of said upper part of said cooling
elements.
2. Air condensation plant according to claim 1, wherein said
cooling elements extend at an inclination toward one another.
3. Air condensation plant according to claim 1, wherein said cover
means are adjustable so as to progressively increase the area of
the side of the respective cooling elements that is covered
thereby, said air flow directing means being adjustable for
reducing the flow of cooling air to the respective side of said
cooling element.
4. Air condensation plant according to claim 1, wherein said
adjustable flaps are pivotable about an axis extending along the
upper inner edge of said cooling elements.
5. Air condensation plant according to claim 1, including a
symmetrical assembly of two of said cooling elements leaning toward
one another at an inclined angle, the adjustable flaps of both said
cooling elements being pivotbale about axes located in the angle
defined by said cooling elements, said flaps, in neutral position
thereof, being suspended substantially vertically.
6. Air condensation plant according to claim 1, wherein said flaps
are provided with parts movable for enlarging the covering area of
said flaps.
7. Air condensation plant according to claim 6, wherein said flaps
are respectively formed of pivotable flap parts and flap parts that
are slidably mounted on said pivotable flap parts.
8. Air condensation plant according to claim 1, wherein said
cooling elements have a lower portion of the respective side
thereof to which the flow of air is directed by said directing
means, said adjustable covering means being located at said lower
portion.
9. Air condensation plant according to claim 8, wherein said
cooling elements each comprise a plurality of cooling tubes spaced
from one another so as to form a flow path for the cooling air
substantially parallel to said cooling tubes.
10. Air condensation plant according to claim 1, wherein said
cooling elements, respectively, have an inlet side for the air flow
directed by said directing means, and a discharge side for the air
flow passing through said cooling elements, and including control
means for issuing control commands for reducing the air flow from
said flow directing means simultaneously with the adjustment of
said covering means.
11. Air condensation plant according to claim 1, including
adjustable covering means located at said discharge side of said
cooling elements, said control means being adapted to issue control
commands for reducing the air flow from said flow directing means
simultaneously with the adjustment of said covering means at said
discharge side of said cooling elements.
12. AIr condensation plant according to claim 10, including a
control device for automatically adjusting said covering means in
dependence upon the variability of a condensation operating
value.
13. Air condensation plant according to claim 12, wherein said
condensation operating value is the condensate temperature, said
adjustment being effective in accordance with said condensate
temperature with respect to the temperature of the outer air and
the temperatures of the cooling air flow at said inlet and outlet
sides of said cooling elements.
14. Air condensation plant according to claim 11, wherein said
control device, in response to said covering means being fully
closed at said inlet side of said cooling elements, and said
cooling air being reduced, is adapted, upon a required further
reduction of the cooling air flow, to adjust said covering means at
said outlet side of said cooling elements in closing sense in
dependence upon the reduction in the cooling air throughput.
15. Air condensation plant according to claim 11, wherein said air
flow directing means is adjustable for reducing the output thereof
to a minimum, said control device being thereby actuable for
simultaneously closing said covering means at said discharge side
of said cooling elements.
16. Air condensation plant according to claim 11, wherein said
control device is connected in a series circuit for closing said
covering means at said inlet side at an initially slight reduction
of the air flow output of said air flow directing means, for
further reducing the air flow after said covering means is
completely closed, and for closing said covering means at said
discharge side after air flow is reduced to a minimum.
Description
The invention relates to air condensation plant for condensing
steam, especially exhaust steam turbines by direct air cooling.
Air condensation plants of this general type have been used with
respect to the cooling surfaces and the quantity of cooling air for
specific operating relationships, for example for measuring total
output of the steam turbine for mean cooling air temperature. At
higher air temperatures, a specific reduction in efficiency must be
taken into consideration because the condensate temperature and
therewith exhaust steam pressure increase to predetermined amount.
In contrast thereto difficulties arise if the condensation plant is
to operate at very low air temperatures and also at very low
loading of the steam turbine, and with quantities of steam that are
reduced with respect to the normal rating therefor. Special
measures must be consequently in order to prevent supercooling or
undercooling of the condensate, especially to avoid danger of
freezing, because damage can otherwise occur to the condensation
plant.
Many efforts have been made heretofore for avoiding danger of
freezing. At first it was suggested that the quantity of cooling
air be reduced by suitably changing the rotary speed or the
position of the blades of the fans or blowers. These measures by
themselves, however, are not adequate in all cases because the
cooling surfaces for a greater temperature difference than
correspond to that for which they are rated continue to be
effective, and a great undercooling of the condensate always occurs
in spite of reduce heat transfer value on the air side, so that one
must take into consideration formation of ice. It would furthermore
be of no help in this case if one were to stop one or all of the
fans or blowers and thereby attain a marked reduction in the
cooling action.
Attempts have therefore been made heretofore to locate the inlet
and discharge sides of the cooling elements and the fan or blower
in a chamber which is in communication with the outer air through
adjusting flaps. When there is danger of freezing, part of the
previously warmed cooling air is thereby returned to the fan or
blower at the inlet side so that the mean cooling air inlet
temperature is always increased to such an extent that no ice
formation can occur. Though danger of freezing can be effectively
avoided in this manner, one must however take into consideration
the coincident marked disadvantages which, in addition to the
significant construction costs, are primarily based upon the fact
that full fan or blower output for cooling is always necessary.
Consideration has also been given heretofore to branch off part of
the cooling air that is being advanced through suitably mounted
flaps with a fan or blower that is being driven at a constant speed
before the cooling elements are traversed by the flow of cooling
air, and to conduct part of the cooling air to the surrounding
atmosphere. But this measure also has a disadvantage in that energy
for advancing the cooling air is unnecessarily consumed, and the
condensation plant is thereby operated uneconomically.
In a heretofore known air condensation plant an attempt has been
made to solve this problem by operating part of the cooling
elements or all of them in the so-called dephlegmator circuit or
system. In this dephlegmator system, the steam flows in the
direction opposite to the condensate in the dephlegmator part so
that the condensate generally cools off to a temperature not much
below the steam temperature. Even if freezing can also be
effectively prevented thereby, nevertheless, such a condensation
plant is again beset by a disadvantage in that the cooling action
is considerably lower then for conventional condensation during
which the steam and the condensate both flow in the same direction.
Such a condensation plant consequently requires a relatively
greater cooling surface and must be accordingly larger, extensive
and costlier.
It has been heretofore also suggested that a part of the cooling
elements be shut down or rendered inactive at reduced turbine
output and lower air temperatures by cutting off the supply of
steam to these cooling elements. However, the relatively large
steam slide valves that are required and that are subjected to
vacuum again call for a high technical outlay, are costly and can
cause operational difficulties.
Another heretofore offered suggestion for reducing freezing has
been to provide additional tubes shorter than the cooling tubes at
a lower part of the cooling tubes of each cooling element at the
inlet of the cooling air thereto, i.e., at the location at which
there is the greatest danger of freezing, those additional
relatively shorter tubes being subjected in the interior thereof to
steam which has been conducted through a throttling member. This
throttling member, however, reduces the condensation pressure and
the condensation temperature therewith, so that the danger of
freezing becomes even greater and the problem at hand remains
unsolved. Also, the simple addition of flaps for covering a part of
the cooling elements has not heretofore permitted the elimination
of danger of freezing.
With the foregoing and other objects in view we provide air
condensation plant for condensing steam by direct air cooling which
comprises mutually transversely disposed elongated cooling elements
traversible by steam along the length thereof, means for directing
a flow of air to a respective side of said cooling elements,
adjustable means for covering the side, respectively, of the
cooling elements for controlling the cooling thereof and for
preventing freezing, the cooling elements having an upper part
through which a preponderant quantity of the steam to be
condensated flows, the adjustable covering means being located in
front of the upper part of the cooling elements.
Further in accordance with the invention the cooling elements are
disposed either perpendicularly or inclined with respect to one
another. Moreover, the adjustable covering means are in the form of
flaps, jalousies, roller blinds or the like.
In view of the construction of the invention in the instant
application, dephlegmator operation of the condensation plant is
dispensed with, and steam and condensate can flow in the same
direction as is conventional for normal condensation plants.
Adjustable flaps that had been heretofore mounted at the cooling
elements were generally located in the lower part or region of the
cooling elements. In these heretofore known plants however icing
occurred and, in fact, frost damage occurred in the cooling tubes
at the level of the upper edge of the flaps because the local
cooling action through a greater air velocity was even stronger
than before due to the heat transfer value improved thereby. No
change occurs therein if the flaps are mounted at the cooling air
discharge or outlet side of the cooling element. Since the lower
half of the cooling tubes is then further subjected to the blast of
the cooling air, danger of freezing is still present at least to
the same extent to the condensate further condensed at the top of
the cooling tubes. If the quantity of cooling air were itself to be
reduced, the cooling action in the upper half of the cooling
elements would, in fact, be diminished and the condensate would
then flow downwardly into the cooling tubes of the lower half of
the cooling elements which are subjected to the blast of the
cooling air and might freeze there. Only when, in accordance with
the invention of the instant application, adjustable covering means
are mounted in the upper part of the cooling elements on the air
inlet side thereof, which covering means more or less greatly cover
the cooling surfaces when there is danger of freezing, can a
supercooling or undercooling of the condensate in the still active
cooling surfaces of the cooling elements be markedly prevented, if
necessary in connection with additional reduction of the cooling
air flow. Since only steam flows upwardly in the upper part of the
cooling elements and the cooling tubes located there are not
subjected to the blast of cooling air which is advanced by the fan
or blower, the cooling effect zone shifts downwardly so that one
does not even have to be concerned any longer with danger of
freezing.
In accordance with the invention, when there is a progressive
increase in the covered surface, the flow of cooling air can be
additionally reduced arbitrarily or automatically by adjusting of
the covering means. The adjustable covering means are formed in a
relatively simple manner by flaps. It is possible however to employ
in place thereof, jalousies or rolling blinds as long as care is
taken that no flutter phenomena occur in the air current.
In accordance with another feature of the invention, we employ
pivotable flaps which are pivotable about an axis extending along
the upper inner edge of the cooling element. When two cooling
elements are disposed so that they are symmetrically inclined with
respect to one another, in accordance with the invention, the pivot
axes for the flaps of both cooling elements are located in the
angle defined by the mutually inclined cooling elements, and
accordingly the flaps are freely suspended in vertical position in
the rest or neutral position thereof. The flaps are additionally
provided, in accordance with another feature of the invention, with
elongating or widening portions in order to increase the covering
surface. Such elongating or widening portions are slidably secured
to the pivotable flaps.
In many cases it is desirable, for example, under extreme
conditions, i.e., very low cooling air temperature, low quantities
of steam and strong wind action, to apply additional measures
against the danger of freezing, also at the outer side of the
cooling elements.
Consequently, in accordance with still another feature of the
invention, we dispose adjustable covering means additionally on the
air outlet side of the cooling elements at a lower part of the
cooling elements.
Advantageously further in accordance with the invention, the
spacing between the cooling tubes in the cooling elements is
increased to such an extent that the cooling air is able to flow
upward and over a greater section of the cooling elements parallel
to the cooling tubes. If desired, the quantity of cooling air
advanced by the fan or blower can thereby be reduced still
further.
With the aid of a central control device, control damages for
continuous or stepwise reduction of the quantity of cooling air can
be given simultaneously with the adjustment of the covering means
on the air inlet side at the upper part of the cooling elements
and, if desired, also with the adjustment of the covering means at
the air discharge side at the lower part of the cooling
elements.
Moreover, it is also possible, in accordance with the invention, to
permit the operations to be carried out automatically by providing,
for example, a control device for automatically adjusting the
covering means in dependence upon the tendency of the condensation
operating values to vary. Thus, for example, the condensate
temperature and possibly also the temperature of the outer air and
of the cooling air upstream and downstream of the passage therefor
through the cooling elements are converted to control signals. From
these temperature values, a remote control or a switch-over to
automatic operation can then take place, as desired.
Other features which are considered as characteristic for the
invention are set forth in the appended claims.
Although the invention is illustrated and described herein as
embodied in air condensation plant, it is nevertheless not intended
to be limited to the details shown, since various modifications and
structural changes may be made therein without departing from the
spirit of the invention and within the scope and range of
equivalents of the claims.
The construction and method of operation of the invention, however,
together with additional objects and advantages thereof will be
best understood from the following description of specific
embodiments when read in connection with accompanying drawing, in
which:
FIGS. 1 and 2 are greatly simplified and partly schematic, vertical
sectional views of two different embodiments of the air
condensation plants of our invention.
Corresponding or similar parts in both of the figures are
identified by the same reference numerals.
Referring now to the drawing and first, particularly to FIG. 1
thereof, there is shown therein, in section, an air condensation
plant according to the invention in which steam that is to be
condensed is passed through a line 1 from which it is distributed
to symmetrically arrayed and downwardly inclined cooling elements 2
and 3. The cooling elements are provided, respectively, with
cooling tubes of which only the longitudinal center lines 4 and 4'
thereof are shown in FIG. 1. The condensate that is formed
accumulates in lower lines 5 and 5'. A fan or blower 6 is located
below the steam line 1 and cooling element 2, 3 assembly and is
driven by an electric motor 7. The entire air condensation plant is
mounted on a platform 8.
In the upper region of the cooling elements 2 and 3, as viewed in
FIG. 1, flaps 9 and 10 are mounted in the angle defined by the
inclined cooling elements 2 and 3. The flap 9 is shown in so-called
neutral or rest position, while the flap 10 covers the upper region
of the cooling element 3. Thus, the cooling element 2, in the
illustrated position of the flap 9 of FIG. 1, is subjected fully
and without change to the cooling flow from the flower 6. As shown
in FIG. 1 by the arrows 11, the cooling air flows in direction onto
the entire length of the cooling element 2 and engages the cooling
tubes 4 along the entire length thereof.
The flap 10 is shown in the position which characterizes the
operation when there is danger of freezing. A suitably reduced
quantity of cooling air then flows in direction of the arrows 12
through only the lower part of the cooling element 3 so that
condensation occurs only in the lower part of the cooling tubes 4.
In the upper part of the cooling tubes 41, which are protected by
the flap 10 from the traversal therethrough of air current from the
blower 6, stream flows downwardly. The flaps 9 and 10 are pivotable
in direction of the arrows 13 and 14; generally both flaps 9 and 10
being simultaneously pivotable. Only in the event of unusual
operating circumstances, for example, if one of the cooling
elements 2 and 3 is exposed to powerful solar irradiation while the
other of the cooling elements is being simultaneously subjected to
a cold wind, can an asymmetrical flap adjustment be made.
In the embodiment of FIG. 2, the air cover flaps are of
multipartite construction. The flap 15, which is shown in neutral
or rest position in FIG. 2, is formed of a pivotable portion 15a
and a portion 15b slideably mounted thereon so as to serve as an
elongation member. The slideable portion 15b, as shown, is slid
alongside almost the entire length of the pivotable portion 15a in
the rest position of the flap 15. On the right-hand side of FIG. 2,
there is shown a flap 17 in a position wherein it is fully pivoted
against the cooling element 3, the flap 17 being formed of a
pivotable flap portion 17a and a slideable elongation portion 17b
mounted thereon and slid into its outermost extending position in
the figure.
Furthermore, pivotable flaps 16 and 18 are mounted at the outside
of the cooling elements 2 and 3 in the lower region, respectively
thereof, in order thereby to counter or offset extreme conditions
of freezing danger. The flap 16 for the cooling element 2 is shown
in normal or neutral position while, in accordance with the
illustrated position of the pivotable flap 17 which is extended
alongside the cooling element 3 is also pivoted into a position
alongside and against the same. An operative means for quite
extreme conditions is thus represented by the layout of the flaps
17 and 18 alongside the cooling element 3.
The spacing a between the cooling tubes 4 of the embodiment of FIG.
2 is enlarged to such an extent with respect to the corresponding
spacing between the cooling tubes 4 of the embodiment of FIG. 1, so
that the cooling air from the blower 6, as represented by the
arrows 12, is able to flow in the cooling element 3 along a
considerable distance parallel to the tubes 4', the flow path of
the cooling air being defined or predetermined by the flaps 17 and
18.
As is furthermore apparent from FIG. 2, automatic adjustment of the
pivotable flaps 15 to 18 is possible in connection with a reduction
in the blower output. Accordingly, a suitable regulating device 20
is provided, which receives measurement signals over signal lines
21 and 22 from suitable condensate temperature measuring sensors
located in the condensate collecting lines or manifolds 5 and 5'.
In addition, a suitable temperature measurement signal controlled
by the outside temperature, is fed to the regulating device 20 over
a signal line 24 from a measuring location 23. Moreover temperature
measurements of supplied and discharged cooling air can be obtained
at suitable locations.
Conventional command transmitters 25, 26 and 27 are connected to
the control device 20 for transmitting adjusting commands that are
represented by the lines of action 28 and 29 for suitably adjusting
the pivotable flaps 15 and 17. Although not illustrated, it is
assumed that suitable telechron or adjustment motors, for example,
are located at the respective pivots of the flaps and are properly
energizable in accordance with the signals transmitted thereto for
adjusting the flaps. Moreover, an action line 30 is shown through
which the pole-reversible or adjustable speed drive motor 7 of the
blower 6 is influenced or adjustably controlled. For extreme
operating conditions, the flaps 16 and 18 are adjustable over the
represented action lines 31 and 32.
When a control system is provided which, with the adjustment of the
covering devices or flaps on the sides of the cooling elements
toward which the air flow is directed, gives off control commands
to reduce the quantity of cooling air, this control system can be
constructed so that after the executed closing of the covering
devices or flaps on the sides toward which the air flow is directed
and after the quantity of cooling air has been diminished, at the
required or demanded further reduction in the quantity of cooling
air, it causes an adjustment of the covering devices on the sides
of the cooling elements from which the air flow is discharged in
the closing sense depending upon the reduction in the air
throughput quantity. Thus, for example, a command to adjust the
covering devices or flaps at the air flow discharge side of the
cooling elements is given as the last stage for constant or
step-wise reduction in the air-blowing output.
A control or regulating device which satisfies these requirements,
can contain a series circuit or sequential connection which, when
the air-blowing power is reduced, first ensures that the upper
covering devices at the sides of the cooling elements to which the
air flow is directed, are increasingly closed. As the next stage,
after the executed full closing of these covering devices, an even
further reduction of the air flow throughput is then produced.
Finally, after attaining adjustment of the air blower output at its
lowest value, the outer covering devices are closed.
One may naturally also propose to assign the adjustment of the
outer covering devices or flaps to a separate regulating device
wherein, for example, the flap adjustment is made dependent upon
the quantity of air throughput. Use may also be made, thereby, of
an automatic adjustment wherein suitable flaps are placed in
neutral or rest position thereof by weight or spring loading in
closed condition and are fully opened only by the cooling air flow.
If the quantity of cooling air should then drop below a specific
minimum value, automatic closing of the covering devices or flaps
is effected by spring force or weight-loading.
* * * * *