U.S. patent application number 11/442008 was filed with the patent office on 2007-11-29 for method and apparatus for covering a pressure vessel.
Invention is credited to Brian John Clark, David Ernest Welch.
Application Number | 20070272687 11/442008 |
Document ID | / |
Family ID | 38622478 |
Filed Date | 2007-11-29 |
United States Patent
Application |
20070272687 |
Kind Code |
A1 |
Clark; Brian John ; et
al. |
November 29, 2007 |
Method and apparatus for covering a pressure vessel
Abstract
An apparatus disclosed herein relates to a pressure vessel cover
comprising, a periphery of the cover, a first surface of the
periphery for sealing on a first side of the cover and a second
surface on a second side of the cover opposite from the first side,
a third surface on the first side of the cover and located radially
inwardly from the periphery, the third surface being displaced
axially from the first surface in the direction of the second
surface, a fourth surface on the second side of the cover radially
inwardly positioned from the periphery, and a bore through the
cover in fluidic communication with the third surface and the
fourth surface.
Inventors: |
Clark; Brian John; (Clifton
Park, NY) ; Welch; David Ernest; (Amsterdam,
NY) |
Correspondence
Address: |
CANTOR COLBURN, LLP
55 GRIFFIN ROAD SOUTH
BLOOMFIELD
CT
06002
US
|
Family ID: |
38622478 |
Appl. No.: |
11/442008 |
Filed: |
May 26, 2006 |
Current U.S.
Class: |
220/4.17 |
Current CPC
Class: |
F16K 27/12 20130101;
F16J 13/02 20130101 |
Class at
Publication: |
220/4.17 |
International
Class: |
B65D 6/00 20060101
B65D006/00 |
Claims
1. A pressure vessel cover, comprising: a periphery of the cover; a
first surface of the periphery for sealing on a first side of the
cover; a second surface on a second side of the cover opposite from
the first side; a third surface on the first side of the cover and
located radially inwardly from the periphery, said third surface
being displaced axially from the first surface in the direction of
the second surface, a fourth surface on the second side of the
cover radially inwardly positioned from the periphery; and a bore
through the cover in fluidic communication with the third surface
and the fourth surface.
2. The pressure vessel cover of claim 1, further comprising: a port
through the cover in fluidic communication with the bore and an
outer circumference of the periphery.
3. The pressure vessel cover of claim 1, further comprising: a
plurality of through holes in the periphery in fluidic
communication with the first surface and the second surface.
4. The pressure vessel cover of claim 1, wherein: an axial distance
from the first surface to the second surface is substantially equal
to an axial distance from the third surface to the fourth
surface.
5. The pressure vessel cover of claim 3, wherein: the first surface
is substantially flat.
6. The pressure vessel cover of claim 5, wherein: the plurality of
holes are substantially perpendicular to the first surface and the
perpendicularity of the plurality of holes is unaltered by an
application of heat and pressure to the third surface.
7. The pressure vessel cover of claim 5, wherein: the third surface
is substantially flat.
8. The pressure vessel cover of claim 7, wherein: the fourth
surface is substantially flat.
9. The pressure vessel cover of claim 8, wherein: the first, third
and fourth surfaces are substantially parallel to each other.
10. A method of distributing stress in a bored pressure vessel
cover, comprising: transmitting stress applied to an interior
surface of the cover surrounding the bore symmetrically to a
thickness of a periphery of the cover.
11. The method of claim 10, further comprising: maintaining
substantially a constant wall thickness throughout the cover.
12. The method of claim 10, further comprising: maintaining
perpendicularity of a plurality of mounting holes through the
periphery with a sealing surface of the periphery throughout
temperature and pressure induced stressing of the cover.
Description
BACKGROUND OF THE INVENTION
[0001] A chamber that contains a fluid within the chamber at higher
pressures than is on an exterior of the chamber is often referred
to as a "pressure vessel." Pressure vessels may be used to house
valves, which control the flow of the fluid through the pressure
vessel. Such fluid flow may be for the transport of steam, for
example, in the case of a steam turbine power plant. Housing the
valves within the pressure vessel makes necessary a cover through
which access to the valves is possible for purposes of servicing
the valves, for example. The cover must form and maintain a seal to
the pressure vessel under the various operating conditions that it
will be subjected to, such as, elevated pressures and temperatures
as well as cycles of varying pressures and temperatures.
[0002] Variable flow "control valves" and only fully-opened or
fully-closed "stop valves" are commonly used in steam turbine power
plants. With the use of these valves it is desirable to have a bore
through the cover to allow for actuation of the valves, through the
bore, from outside of the pressure vessel. Locating the actuator
external to the pressure vessel, improves accessibility to the
actuator, simplifying servicing of the actuator since the seal, of
the cover to the pressure vessel, need not be disturbed.
[0003] Covers that incorporate bores tend to be very thick heavy
plates of metal. Thick covers are used to minimize deformations of
the cover resulting from stresses from pressure loading and from
thermal bending induced from temperature variations across the
thickness of the cover. Large deformations can cause failures of
the bolts, which fastened the cover to the vessel, or the cover
itself, due to low cycle fatigue (LCF), and therefore need to be
minimized.
[0004] Pressure vessel covers with bores have typically been flat
to accommodate and align the valve components that abut surfaces of
the cover. Such components may include an actuator yoke, on the
external surface of the cover, and a balance chamber and bushing
holder, on the interior surface of the cover for example. These
valve components abut flat surfaces surrounding the bore to provide
alignment of the actuator externally and the valve head to valve
seat internally.
[0005] Pressure vessels with thick flat covers with bores, however,
continue to have failures due to stresses. Such failures include
LCF bolt failures that result from the cyclic application of
bending stresses. Some bending stresses occur during turbine start
up when hot steam first reaches the interior surface of the cover.
During this transient condition, the interior surface of the cover
expands with the increase in temperature before the rest of the
cover does. This expansion causes the cover to dish inward toward
the pressure vessel. Such dishing causes a peripheral portion of
the cover, through which the bolts pass, to also dish resulting in
a bending stress being applied to the bolts.
[0006] Conversely, the cover is forced to dish outwardly after the
cover and bolts reach a steady state operating temperature and full
steam pressure is applied to the interior surface. Such dishing, in
the opposite direction than that from the turbine start up
condition, results in a bending stress, on the bolts, in an
opposite direction. Consequently, each start up cycle of the steam
turbine may result in a fatigue cycle of the cover and the bolts,
first in one direction and then in the opposite direction.
[0007] Accordingly there is a need in the art for a pressure vessel
cover that reduces stress on the cover and on the bolts that fasten
the cover to the pressure vessel.
BRIEF DESCRIPTION OF THE INVENTION
[0008] Disclosed is an apparatus that relates to a pressure vessel
cover comprising, a periphery of the cover, a first surface of the
periphery for sealing on a first side of the cover, a second
surface on a second side of the cover opposite from the first side,
a third surface on the first side of the cover and located radially
inwardly from the periphery, said third surface being displaced
axially from the first surface in the direction of the second
surface, a fourth surface on the second side of the cover radially
inwardly positioned from the periphery; and a bore through the
cover in fluidic communication with the third surface and the
fourth surface.
[0009] Further disclosed herein is a method that relates to
distributing stress in a bored pressure vessel cover, comprising,
transmitting stress applied to an interior surface of the cover
surrounding the bore symmetrically to a thickness of a periphery of
the cover.
BRIEF DESCRIPTION OF THE DRAWINGS
[0010] The following descriptions should not be considered limiting
in any way. With reference to the accompanying drawings, like
elements are numbered alike:
[0011] FIG. 1 depicts a partial cross sectional view of a valve
assembly disclosed herein;
[0012] FIG. 2 depicts a perspective view of a cover disclosed
herein; and
[0013] FIG. 3 depicts a cross sectional view of the cover of FIG.
2.
DETAILED DESCRIPTION OF THE INVENTION
[0014] Referring to FIG. 1, a steam valve assembly in accordance
with an embodiment of the invention is generally shown at 10. The
valve assembly 10 includes a valve body 14 with an inlet 18 and an
outlet 22. A seat 26, sealably attached to the body 14, may receive
such as a control valve head 30 or a stop valve head 34. Flow
through the valve 10 from the inlet 18 to the outlet 22 flows
through the annular opening between the heads 30, 34 and the valve
seat 26. Flow of steam is halted when either valve head 30, 34
contacts the seat 26. The stop valve head 34 is actuated through
the stop valve stem 38 by a stop valve actuator (not shown). The
stop valve is designed to be fully opened or fully closed and may
be used as an emergency shut off valve. The control valve head 30
is actuated through control valve stem 42 by a control valve
actuator (not shown). The control valve is designed to allow for
variable levels of closure depending upon how far the control valve
head 30 is from the seat 26. The forgoing construction is sometimes
referred to as an in-line combination valve, since the control
valve and the stop valve share a common axis.
[0015] The control valve stem 42 slidably engages with a bushing 46
pressed into a bore 50 through a cover 54. The control valve
actuator is positioned relative to the cover 54 by an actuator yoke
58 that abuts a yoke surface 62, on the cover 54, thereby aligning
the control valve stem 42 with the bushing 46 and the bore 50. The
yoke surface 62 may be flat to further facilitate aligning the yoke
58 with the bushing 46 and the bore 50. The yoke surface 62 is
substantially perpendicular to the bore 50 and bushing 46. The
perpendicularity provides alignment to the actuator such that the
stem 42 moves through the cover 54 in a perpendicular manner to the
yoke surface 62. The control valve stem 42 is in operable
communication with the head 30 such that movement of the stem 42
results in movement of the head 30, which directly controls the
annular flow area between the head 30 and the valve seat 26. The
annular flow area controls the flow rate of the steam through the
valve 10. Thus control of the flow rate of the steam is directly
controllable by controlling the control valve actuator.
[0016] The control valve may completely stop flow of the steam by
extending the stem 42 and moving the control valve head 30 into
contact with the seat 26. An accurate alignment of the head 30 with
the seat 26 is necessary to assure valve closure as the head 30
contacts the seat 26. Such alignment within the pressure vessel is
provided to the head through a balance chamber 66. The balance
chamber 66 abuts a third surface, also referred to herein as
chamber surface 70, which may be flat, on the interior of the cover
54 that is perpendicular to the bore 50. An exterior cylindrical
wall 80 of the head 34 slidably engages an internal cylindrical
wall 76 of the balance chamber 66, thereby guiding the head 30 in a
direction perpendicular to the flat surface 70. Accordingly, by
making the flat surfaces 70, 62 perpendicular to the bore 50, the
actuator (not shown), the actuator yoke 58, the control valve stem
42, the balance chamber 66 and the head 30 are all kept in
alignment relative to the cover 54. Consequently, the cover 54 is
an important component in maintaining accurate alignment of the
head 30 with the seat 26. The valve body 14 also provides alignment
of the head 30 with the seat 26 since both the seat 26 and the
cover 54 are attached directly to the body 14.
[0017] Referring to FIGS. 2 and 3, the cover 54 has a periphery 74
with a plurality of holes 78 that extend axially therethrough. The
holes 78 receive bolts 82 that threadably engage with threaded
holes 84 in the valve body 14, thereby attaching the cover 54 to
the valve body 14. In addition to the structural attachment of the
cover 54 to the body 14, a sealing of the cover 54 to the body 14
is also achieved. A first surface, referred to herein as sealing
surface 86, which may be flat, on the cover 54, sealably engages
with a seal surface 90 of the opening of the pressure vessel body
14. A gasket (not shown) may also be included between the surfaces
86 and 90 to facilitate sealing. The sealing surfaces 86 and 90 may
be in the same plane as the holes 78 and 84 or may be stepped to a
separate plane without deviating from embodiments of the present
invention.
[0018] Maintaining a seal against the high pressure of the steam
requires uniform distribution of the forces generated by the bolts
82 on the cover 54. A second surface, referred to herein as surface
94, which may be flat, of the cover 54, is substantially
perpendicular to the holes 78 and provides a surface for the heads
of the bolts 82 to seat against. The flat surface 94 is
substantially parallel to the flat surface 86 but is on an opposite
side of the periphery 74 from the seal flat surface 86. All four of
the flat surfaces 62, 70, 86 and 94 are substantially parallel to
one another thereby positioning the bore 50 perpendicular to the
surface of the cover 54 as well as perpendicular to the seal
surface 90 of the body 14 providing alignment of the head 30 with
the seat 26 as described above.
[0019] In addition to providing alignment of the valve components,
the cover also must withstand stresses that arise from the high
temperatures and pressures, to which the internal surfaces of the
cover are subjected. One embodiment of the invention distributes
these stresses by doming the cover 54. Specifically, a central
portion 100 of the cover 54, containing among other things the flat
surfaces 62, 70 and bore 50, is displaced axially from the
periphery 74. A generously curved internal surface 104 connects the
displaced flat surface 70, of the central portion 100, with the
flat surface 86, of the periphery 74. Similarly, a generously
curved external surface 108 connects a flat surface 62, also
referred to herein as a fourth surface, portion of the surface 108,
of the central portion 100, with the flat surface 94, of the
periphery 74. The thickness between the flat surfaces 86 and 94,
the curved surfaces 104 and 108 and the flat surfaces 70 and 62 are
substantially equal to one another. Stated another way, the cover
54 has a substantially constant wall thickness throughout.
[0020] The domed shape of the cover 54 reduces the stresses
throughout the cover 54, as well as the stresses that act on the
bolts 82 when compared to a cover that is flat and not dome shaped.
During heat up, for example, when a cold assembly is exposed to hot
steam, the internal surfaces 70 and 104, which are in direct
contact with the steam, heat up first and thus expand first.
Thermal bending, which may cause a dishing in a flat cover as
described in the background above, does not cause dishing with the
domed cover. Thermal bending does not occur in the domed cover 54
due to the geometry of the domed shape. Specifically, the expanding
internal flat surface 70, for example, is positioned substantially
midway between the flat surfaces 86 and 94 of the periphery 74,
thereby distributing this expansive load symmetrically into the
full thickness of the periphery 74, instead of into the surface 86
alone. By distributing the stress symmetrically there is little
force acting to deform the cover 54 into a dished shape.
Additionally by distributing the load into the center of the
periphery 74 the full thickness of the periphery 74 is resisting
the load resulting in a reduction in the overall stress of the
periphery 74.
[0021] Loading applied to the bolts 82 from the cover 54 is also
reduced by the domed shape of the cover 54. Since, as described
above, the periphery 74 is under less total stress, the periphery
74 does not expand as much. Consequently, bending forces applied to
the bolts 82 by the cover 54 are reduced since the holes 78 remain
parallel to and in alignment with the holes 84, in the body 14.
[0022] The domed shape of the cover 54 also reduces the stresses
generated by pressure acting on the cover 54. This is due to the
increase in stiffness of the cover 54 that results from the domed
shape, which is similar to the stiffening that results when ribbing
is added to any flat shape.
[0023] The improved load distributing characteristics of the cover
54 permit the cover 54 to use a thinner overall thickness and less
total material to fabricate than a flat cover for the same
application. Additionally, since the flat surfaces that may need to
be machined on the domed cover 54 include less total area than a
comparable flat cover, for example, the costs for material, time
and labor to perform such machining operations should also be
less.
[0024] A feature referred to as "leakoff," which allows for the
porting off of high pressure/high temperature steam, is sometimes
desirable during throttling of control valves. Therefore, the domed
cover 54 may include a port 112 in fluidic communication with the
bore 50 and an exterior circumference 116 of the periphery 74. Port
112 also may allow for leakoff of the steam to atmosphere or to a
steam recovery unit through piping (not shown) connected to a
flange 120 bolted to the circumference 116. In the domed cover 54,
the port 112 may be formed at an angle relative to the flat surface
86 in order to avoid fluidically connecting the port 112 to any of
the surfaces 86, 94, 62, 70, 194 and 108.
[0025] Some embodiments of the invention may include some of the
following advantages: less cost to manufacture, less total mass,
less time to fabricate, more durable, longer life, lower stresses
internally and on fastening bolts, internal and external mounting
surfaces for valve component and reduced dishing and bowing.
[0026] While the embodiments of the disclosed method and apparatus
have been described with reference to exemplary embodiments, it
will be understood by those skilled in the art that various changes
may be made and equivalents may be substituted for elements thereof
without departing from the scope of the embodiments of the
disclosed method and apparatus. In addition, many modifications may
be made to adapt a particular situation or material to the
teachings of the embodiments of the disclosed method and apparatus
without departing from the essential scope thereof. Therefore, it
is intended that the embodiments of the disclosed method and
apparatus not be limited to the particular embodiments disclosed as
the best mode contemplated for carrying out the embodiments of the
disclosed method and apparatus, but that the embodiments of the
disclosed method and apparatus will include all embodiments falling
within the scope of the appended claims.
* * * * *