U.S. patent number 3,841,786 [Application Number 05/157,438] was granted by the patent office on 1974-10-15 for method and cooling system for cooling centrifugal pumps.
This patent grant is currently assigned to Sulzer Brothers Ltd.. Invention is credited to Dusan Florjancic.
United States Patent |
3,841,786 |
Florjancic |
October 15, 1974 |
METHOD AND COOLING SYSTEM FOR COOLING CENTRIFUGAL PUMPS
Abstract
The pump zone exposed to the risk of vapor bubble formation is
cooled to eliminate or substantially reduce the risk. The cooling
is accomplished in some embodiments by cooling the surfaces of the
impeller blades from within or without, or in some other
embodiments by cooling the medium being conveyed through the
zone.
Inventors: |
Florjancic; Dusan (Winterthur,
CH) |
Assignee: |
Sulzer Brothers Ltd.
(Winterthur, CH)
|
Family
ID: |
4357577 |
Appl.
No.: |
05/157,438 |
Filed: |
June 28, 1971 |
Foreign Application Priority Data
Current U.S.
Class: |
415/114; 415/108;
415/178; 416/96R; 416/244R; 376/402; 415/116; 416/96A; 416/97R;
416/231A; 976/DIG.200 |
Current CPC
Class: |
F04D
29/588 (20130101); F04D 29/24 (20130101); F04D
3/005 (20130101); G21C 15/243 (20130101); F22D
11/02 (20130101); F04D 9/00 (20130101); F04D
29/669 (20130101); F04D 29/586 (20130101); Y02E
30/30 (20130101); Y02E 30/40 (20130101) |
Current International
Class: |
F04D
29/24 (20060101); F04D 29/18 (20060101); F04D
29/66 (20060101); F04D 3/00 (20060101); F04D
29/58 (20060101); F22D 11/00 (20060101); G21C
15/243 (20060101); F04D 9/00 (20060101); F22D
11/02 (20060101); G21C 15/00 (20060101); F04d
007/00 (); F04d 007/06 (); F04d 009/00 () |
Field of
Search: |
;415/1,112,178,116,DIG.1,177,176,114 ;417/901 ;416/95-97 |
References Cited
[Referenced By]
U.S. Patent Documents
Foreign Patent Documents
|
|
|
|
|
|
|
673,393 |
|
Jun 1952 |
|
GB |
|
475,711 |
|
May 1929 |
|
DD |
|
319,020 |
|
Feb 1930 |
|
GB |
|
920,234 |
|
Nov 1954 |
|
DT |
|
350,836 |
|
Jan 1961 |
|
CH |
|
Other References
Flight; Mar. 16, 1956; Vol. 69, No. 2460; p. 293-294. .
The Gas Turbine; R. Hodge et al.; A Review of Blade-Cooling
Systems; Feb. 1958; p. 396-398..
|
Primary Examiner: Raduazo; Henry F.
Attorney, Agent or Firm: Kenyon & Kenyon Reilly Carr
& Chapin
Claims
What is claimed is:
1. A centrifugal pump for the conveyance of hot fluids wherein the
formation of vapor bubbles in the hot fluids is avoided, said pump
comprising
a casing for flow of a fluid therethrough;
a suction branch adjoining said casing;
an internal casing part defining a central inlet;
a drive shaft journalled in said casing and within said casing part
on a longitudinal axis;
at least one radial flow impeller mounted on said drive shaft, said
impeller having at least one blade extending radially of said shaft
and transversely of the fluid flow, said blade having a forward
flow impinging edge and surfaces within a pump zone adjacent said
blade in which vapor bubbles formation can raise, said edge
extending at an angle to said axis of rotation; and
a cooling system for cooling said zone, said system including at
least one bore extending through said blade, a plurality of
discharge ducts disposed in said blade in communication with said
bore and extending to the surface of said forward flow impinging
edge, and means for supplying coolant to said bore and said ducts
to discharge the coolant out of said blade over said blade surface
in a fluid film into said zone.
2. A centrifugal pump as set forth in claim 1 wherein said blade
includes a porous material portion communicating with said duct and
wherein said discharge ducts are formed in said portion.
3. A centrifugal pump for the conveyance of hot fluids having an
improved suction performance wherein formation of vapor bubbles is
avoided, said pump comprising
a casing defining a central inlet for flow of a hot fluid
therethrough;
a drive shaft journalled in said casing and having bores extending
therethrough;
at least one impeller mounted on said drive shaft, said impeller
having at least one radial pumping blade extending therefrom within
a pump zone adjacent said blade in which vapor bubble formation can
arise, said blade having a forward flow inclined leading impinging
edge and surfaces adjacent said pump zone; and
a cooling system for cooling said zone, said system including a
plurality of ducts disposed in said blade at said forward flow
inclined leading impinging edge, means connected to at least one of
said bores in said shaft for supplying a coolant to said ducts to
cool said blade surfaces in said zone, and means connected to said
ducts for receiving the coolant from said blade and for discharging
the received coolant into at least one other of said bores of said
shaft.
Description
This invention relates to centrifugal pumps and more particularly
to a method of improving the suction performance of centrifugal
pumps.
It has been known that the suction performance of centrifugal pumps
is limited by the vapor stress of the delivered fluid. This feature
is particularly noticeable in pumps for delivering hot water, for
example, boiler feed pumps or circulating pumps for nuclear reactor
plants. For example, boiler feed pumps require relatively expensive
inlet pumps in order to enable to the hot feed water to be supplied
to the impellers of the feed pumps with an adequate positive
pressure. However, if the pressure is too low, vapor bubbles will
occur at hazardous positions of the pump. This results in a
deterioration of the delivery rate of the pump and, in some cases,
causes interruption of the delivery, quite apart from the
associated cavitation damage. The vapor bubbles usually occur at
the leading blade edges and, in pumps with radial impellers, the
bubbles occur on the exterior of the impeller suction eye.
Accordingly, it is an object of the invention to suppress vapor
bubble formation on the impeller blade surface of a pump.
It is another object of the invention to improve the suction
performance of a centrifugal pump.
It is another object of the invention to use relatively small inlet
pumps for a boiler feed pump.
It is another object of the invention to eliminate the need for
inlet pumps in some boiler feed apparatus.
Briefly, the invention provides a method and a cooling system by
which a pump zone of a centrifugal pump exposed to the risk of
vapor bubbles is cooled.
The method of the invention resides in the improvement of the
suction performance of a centrifugal pump by cooling the pump zone
at an impeller blade in which there is a risk of vapor bubble
formation. The method, in one embodiment, cools the surfaces of the
impeller blades exposed to the risk by passing a cooling medium
through the interior of the blade. The cooling medium can either be
discharged out of the blades for recirculation or can be discharged
into the pump zone to flow over the external surfaces of the
blades. In another embodiment, the cooling medium can be injected
into the pump zone from the exterior of the pump casing to admix
with the heated medium being conveyed through the zone so as to
cool the conveyed medium. Also, in another embodiment, the medium
being conveyed can be used for cooling purposes. For example, a
portion of the medium can be extracted from the medium flow
upstream of the pump and then injected into the flow in the pump
zone while at a lower temperature.
The cooling system, in one embodiment, utilizes cooling elements
such as a plurality of ducts which pass through the impeller blades
and carry a cooling medium supplied from any suitable means. These
ducts can be connected with return means for recirculation of the
cooling medium or can be connected to discharge ducts in the blades
for discharging the cooling medium in the pump zone over the
external blade surfaces. In another embodiment, the cooling
elements can be in the form of passages which pass through the pump
casing to inject the cooling medium into the pump zone from outside
the pump. In still another embodiment, the cooling elements can be
connected in parallel by-pass relation with the ducts for directing
a medium to be conveyed through the pump. These elements then
direct a portion of the conveyed medium through a separate path
wherein this portion is maintained at a cooler temperature than the
remainder of the flow and inject the cooled portion back into the
flow in the pump zone.
These and other objects and advantages of the invention will become
more apparent from the following detailed description and appended
claims taken in conjunction with the accompanying drawings in
which:
FIG. 1 illustrates a cross-sectional view of an axial-flow pump
with a duct cooling system for the blades according to the
invention;
FIG. 2 illustrates a cross-sectional view of a radial-flow pump
with film cooling according to the invention;
FIG. 3 illustrates a cross-sectional view of a pump with provision
for cooling the fluid which flows through the hazardous zone
according to the invention;
FIG. 4 illustrates another embodiment of a pump according to FIG. 3
modified in accordance with the invention;
FIG. 5 illustrates a partial section of a leading blade edge of a
blade with film cooling according to the invention;
FIG. 6 illustrates a partial section, corresponding to FIG. 5 and
relating to a blade with duct cooling according to the
invention;
FIG. 7 illustrates a section of a leading blade edge in which the
fluid required for forming the film flows outwardly through porous
material from the interior of the blade according to the invention;
and
FIG. 8 diagrammatically illustrates the circuit of a boiler feed
pump constructed in accordance with the invention.
It is noted that in this application "centrifugal pumps" refers to
all pumps having blades over which delivered fluid flows, for
example, axial-flow pumps, radial-flow pumps and diagonal pumps.
The same flow principles apply to all these pump types.
Referring to FIG. 1, an axial-flow pump which may, for example,
function as the circulating pump for a boiling-water reactor is
provided with a tubular casing 1 defining a central inlet for flow
of a fluid therethrough, a suction branch 2 adjoining the casing
and a bearing 3 in which a drive shaft 4 is journalled. In
addition, a boss 5 of an impeller having blades 6 extending
therefrom is mounted on the end of the drive shaft 4 within the
suction branch 2.
In order to cool the blades, a cooling system is provided. This
system has cooling ducts 7 formed in the blades 6 which connect
through respective ports 8, 9 in the boss 5 to ports 10, 11 at the
end of the shaft 4. The connection may be obtained, for example, in
the illustrated manner, by circumferential grooves 12. The ports
10, 11, in turn, communicate with longitudinal bores 13, 14 in the
shaft 4 which are connected, in a manner not shown, to ducts for
the supply and discharge of a coolant, for example a cooling
fluid.
Referring to FIG. 6, the ducts 7 on the leading edge or forward
flow impinging edge of the blade 6, against which the flow
impinges, can alternatively be constructed by being milled into the
surface of the blade 6. In this case, the ducts 7 are covered with
metallic closure strips 15, affixed by soldering.
In operation, there is a risk of a drop below the vapor pressure of
the fluid and consequent formation of vapor bubbles G at hazardous
positions, which may, for example, have the form illustrated in
broken lines in FIG. 6.
According to the invention, the formation of such vapor bubbles G
is counter-acted by cooling of the zone in which there is a risk of
such bubbles being formed. To this end, a coolant, for example
water, is supplied through the bores 13 at a temperature which is
lower than that of the pumped water. The coolant flows from the
bore 13 through the port 11 and the port 9 into the ducts 7 and is
discharged from the ports 8, 10 and the bore 14. The coolant thus
serves to cool the blade 6 via a heat exchange along and adjacent
the path of the ducts 7.
Referring to FIG 2, a radial-flow pump, for example, the feed pump
of a boiler installation, has a pump casing 20 with a suction
branch 21, a casing cover 22 with a shaft seal 23, integral casing
parts 24, 25, 26 with the first casing part 24 defining a central
inlet and a shaft 27 with radial flow impellers 28 and 29. It will
be understood that the impellers of further stages may adjoin the
impeller 29 but would not normally require any cooling. Further,
each impeller 28, 29 carries a plurality of blades as is known.
The cooling system for this pump cooperates with the shaft seal 23
in that the shaft seal 23 is formed of two parts which define a
chamber 30 therebetween. This chamber 30 connects to a supply line
31 for coolant. The chamber 30 also communicates through bores 32,
formed in a shroud bush 33 of the shaft 27, with a circumferential
groove 34 of the shaft 27. Radial bores 35 extend from the groove
34 into an axial bore 36 of the shaft 27. The axial bore 36
communicates through a radial bore 37 with a circumferential groove
38 in the first impeller 28.
As viewed, the flow-receiving leading blade edges of the impeller
28 are provided with bores 39 which adjoin on the circumferential
groove 38. In addition, bores or ducts 40 extend outwardly from
each bore 39 to the tip edge of the impeller 28. This is more
clearly shown in FIG. 5 wherein a section through a leading blade
edge is taken to disclose the construction of the bores 39 and 40.
This illustration also shows further bores 41 which extend
rearwardly into the zone which is hazarded by the formation of
vapor bubbles.
In the embodiment according to FIGS. 2 and 5, the coolant is
preferably the same fluid as the pump fluid but at a lower
temperature. For example, in a boiler feed pump, it is possible for
the coolant, supplied through the duct 31 and the bores 35, 36, 37
to the bore 39 to be feed water at a temperature lower than that
delivered by the pump.
In this embodiment, the coolant is intermixed with the delivered
fluid by emerging outwardly through the bores 40 and 41 from the
blade and flowing in the form of a fluid film, indicated by arrows
in FIG. 5, along the surface of the blade before being intermixed
with the pumped fluid. In this way, the zone, hazarded by the
formation of gas bubbles, may also be cooled.
Referring to FIG. 7, film cooling can also be obtained by means of
the coolant. For example, the coolant forming the coolant film can
flow through the pores of a sintered material of which the leading
edge of the blade 6 is constructed. The sintered material may form
a strip which extends along at least part of the leading edge of
the blade 6 and is provided with a bore 39', corresponding to the
above described bore 39, for supplying the coolant.
Referring to FIGS. 3 and 4, instead of cooling along the leading
edges of the blades as in the preceeding cases, the external
circumferential zones of the flow can be supplied from stationary
sources to achieve the cooling effect. For example, in the radial
flow pumps of the kind illustrated in FIGS. 3 and 4, the zones in
which there is a risk of vapor bubble formation are disposed mainly
on the external circumference of the inlet cross section of the
impeller. FIG. 3 shows a vapor bubble G of this kind.
As shown in FIG. 3, the pump has a casing 50 and an impeller 51 as
well as a labyrinth seal 53 and a restrictor ring 54 on that side
of the impeller 51 which is nearest to the inlet socket 52. A
chamber 55 which is formed between the labyrinth seal 53 and the
restrictor ring 54 communicates through a duct 56 with a coolant
source (not shown). The coolant, in this case also preferably the
same liquid which is being conveyed but having a lower temperature,
flows from the chamber 55 past the restrictor ring 54 and is then
entrained by the flow delivered by the pump. Under these conditions
the coolant will move in a film along the outer wall of the duct of
the impeller 51 to cool the zone in which there is a risk of a
vapor bubble G being formed.
The pump shown in FIG. 4 differs from the pump illustrated in FIG.
3 solely by the fact that the coolant is supplied through
circumferentially disposed ducts 60 which are formed in a suction
branch 61 of the pump. In this case, there is no need to provide
two seals or one seal and one restrictor position at the front of
the impeller 51' of the pump. In use, the coolant supplied by the
system to the pump cools the outer zone of the suction eye of the
impeller 51', which correponds to the hazard zone G in FIG. 3.
Referring to FIG. 8, the circuit of a feed pump 100 which is, for
example, constructed as illustrated in FIG. 2, and is disposed in a
boiler plant connects with a cooling system so that cooling medium
is supplied to the pump impeller of the first stage. The feed pump
100 is provided with feed water from a feed water tank 101 to which
the feed water is supplied by a condensate pump 102. A low-pressure
preheater 103 is disposed between the condensate pump 102 and the
feed water tank 101 in order to preheat the condensate as is known.
The feed pump 100 delivers feed water through a high-pressure
preheater 104 into a steam boiler 105 in which the water is
evaporated and super-heated. The steam passes from the steam boiler
into a turbine 106, is expanded and then finally passes into a
condenser 107. The condensate formed in the condenser 107 is
returned by the condensate pump 102 into the feed water tank
101.
The cooling system utilizes a duct 109 which branches from a
condensate duct 108 connecting the condensate pump 102 to the feed
water tank 101 upstream of the low pressure preheater 103.
Accordingly, the duct 109 conveys cool condensate which may be used
for cooling the first stage of the feed pump in the manner
described by reference to FIG. 2. If blade cooling is to be
provided in accordance with FIGS. 1 or 6 respectively, a duct 110
may be employed for returning the heated coolant. This duct 110
would then extend into the condensate duct 108 upstream of the
condensate pump 102 as shown in dash-dot lines.
* * * * *