U.S. patent application number 17/041730 was filed with the patent office on 2021-03-18 for reciprocating compressor with improved valve cylinder assembly.
The applicant listed for this patent is Dresser-Rand Company. Invention is credited to Scott J. Delmotte.
Application Number | 20210079908 17/041730 |
Document ID | / |
Family ID | 1000005273046 |
Filed Date | 2021-03-18 |
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United States Patent
Application |
20210079908 |
Kind Code |
A1 |
Delmotte; Scott J. |
March 18, 2021 |
RECIPROCATING COMPRESSOR WITH IMPROVED VALVE CYLINDER ASSEMBLY
Abstract
A reciprocating compressor with an improved valve assembly is
disclosed. Compressor includes a cylinder block having a cylinder
that defines a cylindrical bore extending longitudinally along a
bore axis. Cylinder block includes a hollow chamber extending
longitudinally along a chamber axis, which is non-intersecting
relative to the bore axis. Valve assembly is disposed in hollow
chamber. Valve assembly is made up of an axially-stacked
arrangement of components extending along chamber axis. The
axially-stacked arrangement of components is spaced apart from a
wall that forms a perimeter of the cylinder and is thus free from
mechanical interference with the perimeter of the cylinder.
Inventors: |
Delmotte; Scott J.;
(Mansfield, PA) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Dresser-Rand Company |
Houston |
TX |
US |
|
|
Family ID: |
1000005273046 |
Appl. No.: |
17/041730 |
Filed: |
July 13, 2018 |
PCT Filed: |
July 13, 2018 |
PCT NO: |
PCT/US2018/042007 |
371 Date: |
September 25, 2020 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
|
62662329 |
Apr 25, 2018 |
|
|
|
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F04B 39/10 20130101;
F04B 39/14 20130101; F04B 39/122 20130101 |
International
Class: |
F04B 39/10 20060101
F04B039/10; F04B 39/12 20060101 F04B039/12 |
Claims
1. A reciprocating compressor comprising: a cylinder block
including a cylinder that defines a cylindrical bore extending
longitudinally along a bore axis, the cylinder block including a
hollow chamber extending longitudinally along a chamber axis, which
is non-intersecting relative to the bore axis; and a valve assembly
disposed in the hollow chamber, the valve assembly comprising an
axially-stacked arrangement of components extending along the
chamber axis, the axially-stacked arrangement of components spaced
apart from a wall that forms a perimeter of the cylinder, and thus
free from mechanical interference with the perimeter of the
cylinder.
2. The reciprocating compressor of claim 1, wherein the bore axis
and the chamber axis are mutually orthogonal axes.
3. The reciprocating compressor of claim 1, further comprising a
pair of valve covers affixed to mutually opposed sides of the
cylinder block to retain in axial compression within the hollow
chamber the axially-stacked arrangement of components.
4. The reciprocating compressor of claim 1, further comprising an
inlet passageway formed in the cylinder block, and wherein the
axially-stacked arrangement of components includes a suction valve
in fluid communication with the inlet passageway.
5. The reciprocating compressor of claim 4, further comprising an
outlet passageway formed in the cylinder block, and wherein the
axially-stacked arrangement of components includes a discharge
valve in fluid communication with the outlet passageway.
6. The reciprocating compressor of claim 4, wherein the
axially-stacked arrangement of components includes a spacer
interposed between the suction valve and the discharge valve.
7. The reciprocating compressor of claim 5, further comprising a
passageway arranged to provide fluid communication through the
spacer between the cylindrical bore with the suction valve and the
discharge valve.
8. The reciprocating compressor of claim 4, further comprising a
perimeter fluid seal disposed at a perimeter joint between the
suction valve and the spacer.
9. The reciprocating compressor of claim 5, further comprising a
perimeter fluid seal disposed at a perimeter joint between the
discharge valve and the spacer.
10. The reciprocating compressor of claim 1, wherein the cylinder
comprises a double-action cylinder, wherein the cylinder block
includes a further hollow chamber extending longitudinally along a
further chamber axis, which is non-intersecting relative to the
bore axis, the further chamber axis spaced apart from the chamber
axis along the bore axis.
11. The reciprocating compressor of claim 10, comprising a further
valve assembly disposed in the further hollow chamber, the further
valve assembly comprising a further axially-stacked arrangement of
components extending along the further chamber axis, the further
axially-stacked arrangement of components spaced apart from the
wall that defines the perimeter of the cylinder, and thus free from
mechanical interference with the perimeter of the cylinder.
12. The reciprocating compressor of claim 11, wherein the bore axis
and the further chamber axis are mutually orthogonal axes.
13. The reciprocating compressor of claim 12, comprising a further
pair of valve covers affixed to the mutually opposed sides of the
cylinder block to retain in axial compression within the further
hollow chamber the further axially-stacked arrangement of
components.
14. The reciprocating compressor of claim 10, comprising an inlet
passageway formed in the cylinder block, and wherein the
arrangement of further axially-stacked components includes a
further suction valve in fluid communication with the inlet
passageway.
15. The reciprocating compressor of claim 14, comprising an outlet
passageway formed in the cylinder block, and wherein the further
axially-stacked arrangement of components includes a further
discharge valve in fluid communication with the outlet
passageway.
16. The reciprocating compressor of claim 4, wherein the further
axially-stacked arrangement of components includes a further spacer
interposed between the further suction valve and the further
discharge valve.
17. The reciprocating compressor of claim 15, a further passageway
arranged to provide fluid communication through the further spacer
between the cylindrical bore with the further suction valve and the
further discharge valve.
18. The reciprocating compressor of claim 14, comprising a further
perimeter fluid seal disposed at a perimeter joint between the
further suction valve and the further spacer.
19. The reciprocating compressor of claim 15, comprising a further
perimeter fluid seal disposed at a perimeter joint between the
further discharge valve and the further spacer.
20. The reciprocating compressor of claim 1, wherein the valve
assembly is arranged with a respective tilt angle relative to a
local gravity vector, wherein the tilt angle is in a range from
-90.degree. to 90.degree. relative to the local gravity vector.
Description
[0001] This application claims benefit of the Apr. 25, 2018 filing
date of U.S. provisional application 62/662,329, which is
incorporated by reference herein.
BACKGROUND
1. Field
[0002] Disclosed embodiments are generally related to gas
compressors, and, more particularly to reciprocating compressors
cylinders having an improved valve assembly.
2. Description of the Related Art
[0003] Reciprocating compressors are machines that are
widely-employed in a variety of industrial applications. A
reciprocating compressor includes a body or cylinder defining a
compression chamber and a piston movably disposed within the
cylinder chamber. Linear reciprocating displacement of the piston
within the chamber compresses gas (commonly referred to as
"process" fluid or gas) located within the chamber, which is
subsequently discharged at the increased pressure, such as by way
of valves that may be respectively positioned upon respective valve
seats constructed in the body (e.g., a wall) of the compressor
cylinder that defines a compressor cylinder bore. For various
considerations, it is desirable to further improve the
maintainability, durability and overall reliability of the
compressor cylinder design. See U.S. Pat. Nos. 5,209,647 and
5,011,383 for respective examples of reciprocating compressors
involving valve assemblies.
BRIEF DESCRIPTION OF THE DRAWINGS
[0004] FIG. 1 is fragmentary side view of a prior art valve design
for a reciprocating compressor.
[0005] FIGS. 2 and 3 respectively illustrate a fragmentary side
view and a fragmentary end view of one nonlimiting embodiment of a
disclosed valve assembly arranged vertically in a reciprocating
compressor.
[0006] FIG. 4 corresponds to the fragmentary end view shown in FIG.
3, where the disclosed valve assembly is omitted to better
appreciate spatial relationships between a hollow chamber where the
valve assembly is disposed and a cylindrical bore, where a piston
is accommodated.
[0007] FIG. 5 illustrate a fragmentary end view of another
nonlimiting embodiment of a disclosed valve assembly arranged
horizontally in a reciprocating compressor.
[0008] FIGS. 6 and 7 respectively illustrate fragmentary side views
of non-limiting embodiments of inlet or outlet passageways, as may
be constructed in the cylinder block of the reciprocating
compressor shown in FIG. 5.
DETAILED DESCRIPTION
[0009] The inventor of the present invention has recognized certain
issues in connection with certain prior art designs directed to
reciprocating compressor cylinders. FIG. 1 is illustrative of one
such prior art valve compressor design. These prior art designs
typically involve a compressor valve 100 positioned upon a feature
102 (e.g., a valve seat, indent, notch, etc.) constructed in a body
104 (e.g., a wall) of the compressor cylinder that defines a
compressor cylinder bore 106. A substantial magnitude of force is
generally required from a valve cap 108 to hold the valve in place
and resist the differential pressure (e.g., in certain applications
this pressure can reach 10,000 psi and higher) that is formed
between cylinder bore 106 and a valve passage 110. This substantial
force can lead to highly concentrated mechanical stresses on the
valve seat. These stresses tend to limit the cylinder pressure
capabilities and can often lead to structural failure at valve seat
102 and/or compressor cylinder wall 104 from overstress conditions.
Overstress can occur due to a variety of reasons, such as from
variable pressure conditions during operation of the compressor,
over-torque of the valve cover studs during deployment or
servicing, etc.
[0010] Thick valve seats 102--constrained to the smallest size
valve possible in a given implementation--have been proposed to
attempt to alleviate the stress concentration by limiting the
surface area for the pressure to act upon. However, there are
practical limits where even a thicker valve seat no longer provides
practical stress reduction, and thus resulting in suboptimal
capability for the maximum pressure that can be reliably
accommodated in such prior art compressor cylinder designs.
[0011] In view of such recognition, the present inventor proposes
an innovative valve assembly effective to provide a reliable and
relatively low-cost technical solution to solve at least the issues
mentioned above.
[0012] In the following detailed description, various specific
details are set forth in order to provide a thorough understanding
of such embodiments. However, those skilled in the art will
understand that disclosed embodiments may be practiced without
these specific details that the aspects of the present invention
are not limited to the disclosed embodiments, and that aspects of
the present invention may be practiced in a variety of alternative
embodiments. In other instances, methods, procedures, and
components, which would be well-understood by one skilled in the
art have not been described in detail to avoid unnecessary and
burdensome explanation.
[0013] Furthermore, various operations may be described as multiple
discrete steps performed in a manner that is helpful for
understanding embodiments of the present invention. However, the
order of description should not be construed as to imply that these
operations need be performed in the order they are presented, nor
that they are even order dependent, unless otherwise indicated.
Moreover, repeated usage of the phrase "in one embodiment" does not
necessarily refer to the same embodiment, although it may. It is
noted that disclosed embodiments need not be construed as mutually
exclusive embodiments, since aspects of such disclosed embodiments
may be appropriately combined by one skilled in the art depending
on the needs of a given application.
[0014] The terms "comprising", "including", "having", and the like,
as used in the present application, are intended to be synonymous
unless otherwise indicated. Lastly, as used herein, the phrases
"configured to" or "arranged to" embrace the concept that the
feature preceding the phrases "configured to" or "arranged to" is
intentionally and specifically designed or made to act or function
in a specific way and should not be construed to mean that the
feature just has a capability or suitability to act or function in
the specified way, unless so indicated.
[0015] FIGS. 2 and 3 respectively illustrate a fragmentary side
view and a fragmentary end view of a reciprocating compressor 10
that can benefit from a disclosed valve assembly 20. Reciprocating
compressor 10 may comprise a cylinder block 12 including a cylinder
that defines a cylindrical bore 14 extending longitudinally along a
bore axis 16. For simplicity of illustration and to avoid visual
cluttering, elements which are superfluous relative to disclosed
embodiments have been omitted. For example, omitted elements
include cylinders heads, piston and piston rod components. Cylinder
block 12 includes a hollow chamber 15 (FIG. 4) extending
longitudinally along a chamber axis 18, which is non-intersecting
relative to bore axis 16. Without limitation, valve assembly 20 is
disposed in hollow chamber 15.
[0016] Without limitation, valve assembly 20 comprises an
axially-stacked arrangement of components extending along chamber
axis 18. The axially-stacked arrangement of components is spaced
apart from a wall 22 that forms a perimeter of the cylinder, and
thus is free from mechanical interference with the perimeter of the
cylinder. A pair of valve covers 24, 26 may be affixed via suitable
affixing means 27 (e.g., bolts) to mutually opposed sides 28, 30 of
cylinder block 12 to retain in axial compression within the hollow
chamber the axially-stacked arrangement of components.
[0017] In one non-limiting embodiment, an inlet passageway 32 may
be formed in cylinder block 12. In one non-limiting embodiment, the
axially-stacked arrangement of components includes a suction valve
34, as may be located downstream from a respective valve cage 36.
Suction valve 34 is in fluid communication with inlet passageway
32, (as schematically represented by arrows 37).
[0018] In one non-limiting embodiment, an outlet passageway 38 may
also be formed in cylinder block 12. In one non-limiting
embodiment, the axially-stacked arrangement of components includes
a discharge valve 40 as may be located upstream from a respective
valve cage 42. Discharge valve 40 is in fluid communication with
outlet passageway, (as schematically represented by arrows 43).
[0019] In one non-limiting embodiment, the axially-stacked
arrangement of components includes a spacer 44 interposed between
suction valve 34 and discharge valve 40. A passageway 45 (FIG. 3)
is arranged in cylinder block 12 to provide fluid communication
through spacer 44 between cylindrical bore 14 with suction valve 34
and discharge valve 40.
[0020] In one nonlimiting embodiment, a perimeter fluid (e.g., gas)
seal 46 (FIG. 3) is disposed at a perimeter joint 47 between
suction valve 34 and spacer 44. Similarly, a perimeter fluid seal
48 is disposed at a perimeter joint 50 between discharge valve 40
and spacer 44. This seal arrangement is different than in the prior
art design, which is commonly arranged to seal on the face of the
valve. Without limitation, examples of high-pressure seal
arrangements that may be used may include O-rings, Chevron seal
arrangements, such as may involve composite metal/polymer Chevron
sealing arrangements; non-metallic C-seals, T-seals, labyrinth
seals; piston rings seals, etc.
[0021] In one nonlimiting embodiment, the cylinder may comprise a
double-action cylinder, and cylinder block 12, may include a
further hollow chamber extending longitudinally along a further
chamber axis 18' (FIG. 2), which is non-intersecting relative to
bore axis 16. Without limitation, further chamber axis 18' is
spaced apart from chamber axis 18 along bore axis 16. Bore axis 16
and further chamber axis 18' may be mutually orthogonal axes.
[0022] A further valve assembly 20' (FIG. 2) may be disposed in the
further hollow chamber. The further valve assembly 20' may comprise
a further axially-stacked arrangement of components extending along
further chamber axis 18'. As discussed in the context of valve
assembly 20, the further axially-stacked arrangement of components
is spaced apart from wall 22 that defines the perimeter of the
cylinder and is thus free from mechanical interference with the
perimeter of the cylinder. A further pair of valve covers 24', 26'
may be affixed to the mutually opposed sides 28, 30 of cylinder
block 12 to retain in axial compression within the further hollow
chamber the further axially-stacked arrangement of components.
[0023] Without limitation, the arrangement of further
axially-stacked components that makes up valve assembly 20'
includes a further suction valve 34', as may be located downstream
from a respective valve cage 36'. Further suction valve 34' is in
fluid communication with inlet passageway 32, (as schematically
represented by arrows 37' (FIG. 2)).
[0024] In one non-limiting embodiment, the further axially-stacked
arrangement of components that makes up valve assembly 20' includes
a further discharge valve 40', as may be located upstream from a
respective valve cage 42'. Further discharge valve 40' is in fluid
communication with outlet passageway, (as schematically represented
by arrows 43' FIG. 3)). The further axially-stacked arrangement of
components includes a further spacer 44' interposed between further
suction valve 34' and further discharge valve 40'. A further
passageway (analogous to passage way 45 in FIG. 3)) is arranged to
provide fluid communication through the further spacer 44' between
cylindrical bore 14 with further suction valve 34' and further
discharge valve 40'.
[0025] A further perimeter fluid seal 46' is disposed at a
perimeter joint 47' between further suction valve 34' and further
spacer 44'. Similarly, a further perimeter fluid seal 48' disposed
at a perimeter joint 50' between the discharge valve 40' and
further spacer 44'.
[0026] In one non-limiting embodiment, as may be appreciated in
FIGS. 2 and 3, respective chamber axes 18 and 18' may be vertical
axes and valve assemblies 20 and 20' may be vertically arranged.
Without limitation, chamber axes 18 and 18' may be in
correspondence with a local gravity vector; and thus, in this case,
mutually opposed sides 28, 30 of cylinder block 12 would define
respective top and bottom sides of cylinder block 12.
[0027] It will be appreciated, however, that chamber axes 18 and
18' need not be vertically positioned, and, without limitation,
valve assemblies 20 and 20' may be horizontally arranged, as can be
appreciated in FIG. 5. In this case, valve assembly 20 extends
horizontally along chamber axis 18, which in this example is
horizontally positioned. Without limitation, in this case chamber
axes 18 and 18' would be transverse with respect to a local gravity
vector; and thus, in this case, mutually opposed sides 28, 30 of
cylinder block 12 would define respective lateral sides of cylinder
block 12. Valve assembly 20' would be similarly positioned as valve
assembly 20. As would be appreciated by one skilled in the art, an
observer from behind the plane of the paper (that shows FIG. 5)
would view valve assembly 20' in the same manner that valve
assembly is seen in FIG. 5. It is contemplated that chamber axes 18
and 18' need not necessarily be vertically, or horizontally
positioned, and, could be positioned at a respective angle in a
range from -90.degree. to 90.degree. relative to the local gravity
vector. Accordingly, without limitation, valve assemblies 20 and
20' may be arranged with a respective tilt angle relative to the
local gravity vector. That is, at a respective angle in a range
from -90.degree. to 90.degree. relative to the local gravity
vector.
[0028] FIGS. 6 and 7 illustrates respective side views of
non-limiting examples of inlet passageway 32 or outlet passageway
38 as may be constructed in cylinder block 12. For example, at
least respective portions of inlet passageway 32 or outlet
passageway 38 may respectively comprise a respective angled
arrangement, as shown in FIG. 6. Alternatively, at least respective
portions of inlet passageway 32 or outlet passageway 38 may
respectively comprise a T-shaped arrangement, as shown in FIG.
7.
[0029] In operation, disclosed embodiments effectively provide an
arrangement of individual components (e.g., respective valve cages
36, 42, respective valves such as suction valves 34 and discharge
valves 40) loaded axially in compression with each other to form a
self-supporting valve assembly. Advantageously, disclosed
embodiments do not involve features in the cylinder wall for
retaining any of the stacked components.
[0030] Without limitation, outlet passageway 38 may be located at
the bottom of the cylinder (at a lower location relative to inlet
passageway 32) to prevent (e.g., by way of gravity action) possible
accumulation of liquids in the cylinder. Communication of the gas
to the external cylinder connections may be accomplished through
the use of standard machined gas passages constructed using
techniques well-understood to those skilled in the art.
[0031] FIGS. 2 and 3 illustrate the use of one axially-stacked
valve assembly per end of a given double acting cylinder. It will
be appreciated that other alternate embodiments may be realized
depending on the needs of a given application. For example, one
could arrange multiple assemblies on one or both ends of the
compressor cylinder.
[0032] It should now be appreciated that the disclosed valve
assembly relocates the valves (and associated components) to a
location spaced apart from the cylinder. Advantageously, this
location is free from any mechanical interference or impingement
with cylinder features, as would be the case in prior art designs
that involve features (e.g., valve seat, notch, etc.) constructed
in the body of the cylinder to support the valves.
[0033] The force necessary to hold the respective valves against
the differential pressure of the cylinder is applied to a
purely-axial stack of individual components, none of which impinge
upon features in the cylinder wall that defines the cylinder bore.
In disclosed embodiments, the concept of features that define a
valve seat constructed in the cylinder body is no longer
applicable. Accordingly, the above-described pressure limitation of
prior art cylinder designs resulting from the valve seat stresses
is overcome. The arrangement of axially-stacked valve assembly
involves a pair of valve covers disposed at mutually opposed axial
ends of the assembly. Thus, the anchoring of the axially-stacked
valve assembly is fully independent from features in the body of
the cylinder.
[0034] In operation, disclosed embodiments provide a cost-effective
and reliable technical solution to solve a significant operational
issue related to high pressure cylinder operation. Disclosed
embodiments are believed to be effective for reliably supplying
relatively higher pressures in, for example, double-acting
cylinders than have been achievable prior to the present
invention.
[0035] While embodiments of the present disclosure have been
disclosed in exemplary forms, it will be apparent to those skilled
in the art that many modifications, additions, and deletions can be
made therein without departing from the scope of the invention and
its equivalents, as set forth in the following claims.
* * * * *