U.S. patent application number 10/430985 was filed with the patent office on 2003-10-16 for an axially rotated valve and method.
This patent application is currently assigned to Bighorn Valve, Inc.. Invention is credited to Burgess, Robert K., Lindberg, William R., Walrath, David E..
Application Number | 20030192593 10/430985 |
Document ID | / |
Family ID | 27092782 |
Filed Date | 2003-10-16 |
United States Patent
Application |
20030192593 |
Kind Code |
A1 |
Walrath, David E. ; et
al. |
October 16, 2003 |
AN AXIALLY ROTATED VALVE AND METHOD
Abstract
The present invention provides an axially-rotated valve which
permits increased flow rates and lower pressure drop (characterized
by a lower loss coefficient) by using an axial eccentric split
venturi with two portions where at least one portion is rotatable
with respect to the other portion. The axially-rotated valve
typically may be designed to avoid flow separation and/or
cavitation at full flow under a variety of conditions. Similarly,
the valve is designed, in some embodiments, to produce streamlined
flow within the valve. A typical cross section of the eccentric
split venturi may be non-axisymmetric such as a semicircular cross
section which may assist in both throttling capabilities and in
maximum flow capacity using the design of the present invention.
Such a design can include applications for freeze resistant
axially-rotated valves and may be fully-opened and fully-closed in
one-half of a complete rotation. An internal wide radius elbow
typically connected to a rotatable portion of the eccentric venturi
may assist in directing flow with lower friction losses. A valve
actuator may actuate in an axial manner yet be uniquely located
outside of the axial flow path to further reduce friction losses. A
seal may be used between the two portions that may include a
peripheral and diametrical seal in the same plane.
Inventors: |
Walrath, David E.; (Laramie,
WY) ; Lindberg, William R.; (Laramie, WY) ;
Burgess, Robert K.; (Sheridan, WY) |
Correspondence
Address: |
SANTANGELO LAW OFFICES, P.C.
125 SOUTH HOWES, THIRD FLOOR
FORT COLLINS
CO
80521
US
|
Assignee: |
Bighorn Valve, Inc.
Sheridan
WY
|
Family ID: |
27092782 |
Appl. No.: |
10/430985 |
Filed: |
May 6, 2003 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
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10430985 |
May 6, 2003 |
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09941080 |
Aug 27, 2001 |
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6557576 |
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09941080 |
Aug 27, 2001 |
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09619347 |
Jul 19, 2000 |
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6279595 |
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09619347 |
Jul 19, 2000 |
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08925535 |
Sep 8, 1997 |
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6109293 |
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08925535 |
Sep 8, 1997 |
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08637203 |
Apr 24, 1996 |
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5718257 |
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Current U.S.
Class: |
137/360 ;
251/304 |
Current CPC
Class: |
E03B 9/02 20130101; F16K
3/085 20130101; E03B 9/025 20130101; Y10T 137/0396 20150401; Y10T
137/698 20150401; F16K 1/22 20130101 |
Class at
Publication: |
137/360 ;
251/304 |
International
Class: |
F16K 003/02 |
Claims
We claim:
1. An axially-rotated split venturi valve comprising: a. at least
one rotatable sleeve; b. a fixed position sleeve fluidicly
connected to said rotatable sleeve; c. an axial eccentric split
venturi having a first portion and a second portion wherein said
first portion is located inside said fixed sleeve and said second
portion is located inside said rotatable sleeve; d. an exit port
fluidicly connected to said rotatable sleeve; e. a conduit in which
said rotatable sleeve and said fixed position sleeve are located
having a flow path; f. an interface between said rotatable sleeve
and said fixed sleeve; g. a first seal between said rotatable
sleeve and said fixed sleeve at said interface wherein said
rotatable sleeve, said fixed position sleeve, said axial eccentric
split venturi, said exit port, said conduit, said interface and
said first seal comprise an axially-rotated split venturi
valve.
2. An axially-rotated split venturi valve as described in claim 1
further comprising an axial rotator outside of said flow path
adapted to rotate said rotatable sleeve without substantial
engagement of said axial rotator to said rotatable sleeve within
said flow path.
3. An axially-rotated split venturi valve as described in claim 1
wherein said axial eccentric split venturi comprises a semicircular
eccentric split venturi primarily in the proximity of said
interface.
4. An axially-rotated split venturi valve as described in claim 1
further comprising an axial compression member adapted to bias said
rotatable sleeve and said fixed position sleeve toward each
other.
5. An axially-rotated split venturi valve as described in claim 1
wherein said rotatable sleeve is adapted to substantially avoid
cavitation throughout said rotatable sleeve of said valve beginning
at said interface.
6. An axially-rotated split venturi valve as described in claim 1
wherein said valve is adapted to establish a loss coefficient of 4
or less.
7. An axially-rotated split venturi valve as described in claim 1
further comprising a separation in said conduit adapted to create a
thermally insulative barrier in said conduit at said
separation.
8. An axially-rotated split venturi valve as described in claim 1
wherein said first seal comprises an outer periphery seal and a
diametrical seal in substantially the same plane as said outer
periphery seal.
9. An axially-rotated split venturi valve as described in claim 1
wherein said valve comprises a freeze resistant, axially-rotated
split venturi valve comprising a first seal at an interface between
said first and second portions located a freeze distance away from
freezing conditions.
10. An axially-rotated split venturi valve as described in claim 1
wherein said rotatable sleeve comprises a length sufficient to
substantially eliminate flow separation through said rotatable
sleeve.
11. An axially-rotated split venturi valve as described in claim 1
wherein said rotatable sleeve is longer than said fixed position
sleeve.
12. An axially-rotated split venturi valve as described in claim 1
further comprising an exit port fluidicly connected to at least one
of said sleeves and further comprising an internal elbow.
13. An axially-rotated split venturi valve as described in claim 12
further comprising an exit port seal at an exit port interface
between said exit port and a valve outlet fluidicly connected to
said valve.
14. An axially-rotated split venturi valve as described in claim 1
further comprising a cartridge assembly adapted for insertion in
said conduit comprising at least one of said sleeves.
15. An axially-rotated split venturi valve as described in claim 14
further comprising a cartridge seal assembly around said cartridge
assembly adapted to seal cartridge assembly in said conduit.
16. An axially-rotated split venturi valve as described in claim 1
wherein said first seal comprises a curvilinear diametrical
seal.
17. An axially-rotated split venturi valve as described in claim 1
wherein said conduit comprises a flexible tube.
18. An axially-rotated split venturi valve as described in claim 1
wherein said rotatable sleeve in cooperation with said fixed
position sleeve is adapted to be fully opened and fully closed in
one half complete rotation.
19. An axially-rotated split venturi valve as described in claim 1
further comprising a purge port assembly adapted to open and allow
drainage of said valve when said valve is in at least a partially
closed position.
20. A method of improving flow from an axially-rotated valve using
a split venturi comprising: a. flowing through a flow path having a
pressure and velocity; b. entering a first portion of an eccentric
split venturi; c. gradually reducing said pressure of said flow
while increasing said velocity of said flow through said first
portion of said eccentric split venturi; d. flowing across an
interface of said split venturi between said first portion and a
second portion; e. gradually increasing said pressure of said flow
while decreasing said velocity of said flow through said second
portion of said eccentric split venturi; f. exiting said second
portion through an exit port fluidicly connected to said second
portion; g. axially rotating said second portion of said split
venturi to at least a partially closed position; h. at least
partially restricting said flow from flowing through said valve at
said interface; i. rotating said second portion of said split
venturi to at least a partially open position; j. allowing said
flowing of said fluid through said axially-rotated valve.
21. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein said axially rotating said second
portion comprises axially rotating said second portion with an
axial rotator outside of said flow path without substantial
interference with flow efficiency.
22. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein flowing across an interface comprises
flowing through a semicircular eccentric flow path.
23. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising assisting said sealed
interface with an axial pressure element.
24. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein gradually increasing said pressure of
said flow while decreasing said velocity of said flow comprises
avoiding cavitation of said flow.
25. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising establishing a loss
coefficient of 4 or less through said axially-rotated valve.
26. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein flowing through a flow path comprises
flowing through a thermally conductive conduit and further
comprising: a. providing a separation in said thermally conductive
conduit in a freezing zone wherein said separation creates a first
conduit section and a second conduit section of said conduit; and
b. thermally breaking said first conduit section from said second
conduit section in a freeze zone.
27. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising sealing at said interface
comprising: a. sealing about a periphery of said interface between
said portions; b. sealing across a diametrical portion of said
interface in the same plane as said sealing about said
periphery.
28. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising resisting the freezing of
said valve.
29. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising flowing through a length
of said second portion sufficient to substantially eliminate flow
separation through said second portion.
30. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising flowing through a longer
flow path in said second portion than said first portion.
31. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising exiting said second
portion through an exit port comprising exiting through an internal
elbow to a valve outlet fluidicly connected to said valve.
32. A method of improving flow from an axially-rotated valve as
described in claim 31 further comprising sealing at said exit port
between said internal elbow and said valve outlet.
33. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein said flowing through said flow path
comprises flowing through a conduit and further comprising
inserting at least one of said portions as a cartridge assembly in
said conduit.
34. A method of improving flow from an axially-rotated valve as
described in claim 33 further comprising sealing said cartridge
assembly in said conduit.
35. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising sealing said second
portion with said first portion with a curvilinear diametrical seal
at said interface.
36. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein said conduit comprises a flexible
tube.
37. A method of improving flow from an axially-rotated valve as
described in claim 20 wherein axially rotating from a closed
position to an open position comprises axially rotating said second
portion approximately one half turn.
38. A method of improving flow from an axially-rotated valve as
described in claim 20 further comprising purging said
axially-rotated valve in at least a partially closed position.
39. A method of providing improved flow from a valve using a split
venturi comprising: a. flowing a fluid through a flow path with a
pressure and velocity along a central axis; b. gradually reducing
said pressure of said fluid while increasing said velocity of said
fluid through a first portion of a split venturi wherein said first
portion is non-axisymmetric relative to said central axis; c.
gradually increasing said pressure of said fluid while decreasing
said velocity of said fluid through a second portion of said split
venturi wherein said second portion is non-axisymmetric relative to
said central axis; d. rotating at least one of said portions of
said split venturi to at least a partially closed position; e. at
least partially restricting said fluid from flowing through said
valve; f. rotating at least one of said portions of said split
venturi to at least a partially open position; g. allowing said
flowing of said fluid.
40. A method of providing improved flow from a valve as described
in claim 39 wherein flowing said fluid comprises flowing through a
semicircular eccentric non-axisymmetric flow path.
41. A method of providing improved flow from a valve as described
in claim 39 wherein rotating at least one of said portions
comprises axially rotating said portion about a longitudinal axis
parallel to said central axis.
42. A method of providing improved flow from a valve as described
in claim 39 wherein rotating at least one of said portions of said
split venturi to at least a partially closed position further
comprises axially rotating said second portion relative to said
first portion and controlling flowing through said relative
rotation.
43. A method of providing improved flow from a valve as described
in claim 39 wherein rotating comprises axially rotating while
maintaining a fixed longitudinal position of said rotated
portion.
44. A method of providing improved flow from a valve as described
in claim 39 further comprising at least partially sealing at an
interface between said first and second portions.
45. A method of providing improved flow from a valve as described
in claim 39 further comprising rotating a second portion longer
than first portion.
46. A method of providing improved flow from a valve as described
in claim 39 wherein said rotating at least one of said portions
comprises rotating an internal elbow connected to said portion.
47. A method of providing improved flow from a valve as described
in claim 39 further comprising exiting said second portion through
an exit port and sealing said exit port with an exit port seal at
an exit port interface between said exit port and a valve outlet
fluidicly connected to said valve.
48. A method of providing improved flow from a valve as described
in claim 39 wherein rotating at least one of said portions
comprises axially rotating said portion with an axial rotator
outside of said flow path without substantial interference with
flow efficiency.
49. A method of providing improved flow from a valve as described
in claim 39 wherein said flowing said fluid through said flow path
comprises flowing through a conduit and further comprising
inserting at least one of said portions as a cartridge assembly in
said conduit.
50. A method of providing improved flow from a valve as described
in claim 39 further comprising sealing at an interface between said
portions and assisting said interface with an axial pressure
element.
51. A method of providing improved flow from a valve as described
in claim 39 further comprising flowing through a length sufficient
to substantially eliminate flow separation through said second
portion.
52. A method of providing improved flow from a valve as described
in claim 39 wherein flowing said fluid comprises flowing through a
thermally conductive conduit and further comprising: a. providing a
separation in said thermally conductive conduit in a freezing zone
wherein said separation creates a first conduit section and a
second conduit section of said conduit; and b. thermally breaking
said first conduit section from said second conduit section in a
freeze zone.
53. A method of providing improved flow from a valve as described
in claim 39 wherein gradually increasing said pressure of said flow
while decreasing said velocity of said flow comprises avoiding
cavitation of said fluid.
54. A method of providing improved flow from a valve as described
in claim 39 further comprising establishing a loss coefficient of 4
or less through said valve.
55. A method of providing improved flow from a valve as described
in claim 39 further comprising resisting the freezing of said valve
by sealing at said interface a freeze distance away from freezing
conditions.
56. A split venturi valve comprising: a. a conduit having a central
axis and a flow path; b. a first portion of a split venturi wherein
at least a part of said first portion is non-axisymmetric relative
to said central axis; c. a second portion of a split venturi
wherein at least a part of said second portion is non-axisymmetric
relative to said central axis.
57. A split venturi valve as described in claim 56 wherein said
portions of said split venturi comprise an eccentric flow
surface.
58. A split venturi valve as described in claim 56 wherein said
part of said first and second portion of said split venturi that is
non-axisymmetric comprises an eccentric semicircle.
59. A split venturi valve as described in claim 56 wherein said
second portion comprises a rotatable second portion relative to
said first portion adapted to control a flow through said
conduit.
60. A split venturi valve as described in claim 56 further
comprising a first seal located between said first and second
portions in a transition flow zone.
61. A split venturi valve as described in claim 56 further
comprising an internal elbow connected to one of said portions.
62. A split venturi valve as described in claim 56 further
comprising an exit port connected to one of said portions and an
exit port seal at an exit port interface between said exit port and
a valve outlet fluidicly connected to said valve.
63. A split venturi valve as described in claim 56 wherein said
valve comprises an axially-rotated valve.
64. A split venturi valve as described in claim 56 further
comprising an axial rotator outside of said flow path adapted to
rotate at least one of said portions without substantial engagement
of said portion within said flow path.
65. A split venturi valve as described in claim 56 further
comprising a cartridge assembly adapted for insertion in said
conduit comprising at least one of said portions.
66. A split venturi valve as described in claim 56 further
comprising an axial compression member adapted to bias said
portions toward each other.
67. A split venturi valve as described in claim 56 wherein at least
one of said portions comprises a length sufficient to substantially
eliminate flow separation through said portion.
68. A split venturi valve as described in claim 56 wherein said
second portion is longer than said first portion.
69. A split venturi valve as described in claim 56 further
comprising a separation in said conduit adapted to create a
thermally insulative barrier in said conduit at said
separation.
70. A split venturi valve as described in claim 56 wherein at least
one of said portions of said valve is adapted to substantially
prevent cavitation throughout said portion beginning at an
interface between said first and second portions.
71. A split venturi valve as described in claim 56 wherein said
valve is adapted to establish a loss coefficient of 4 or less.
72. A split venturi valve as described in claim 56 wherein said
valve comprises a freeze resistant, axially-rotated valve
comprising a first seal at an interface between said first and
second portions located a freeze distance away from freezing
conditions.
73. A method of providing improved flow from a valve using a split
venturi comprising: a. establishing a flow through a flow path in
at least a portion of an axially-rotated valve having a central
axis; b. controlling said flow between a first and second portion
of a split venturi wherein said portions are fluidicly connected to
said valve; c. axially rotating at least one of said portions of
said split venturi to a rotated position about a longitudinal axis
parallel to said central axis to at least a partially closed
position; d. at least partially restricting said flow; e. axially
rotating said rotated portion of said split venturi about said
longitudinal axis to at least a partially open position; f.
continuing said flow through said valve wherein axially rotating
said portions of said split venturi comprises axially rotating said
portion with an axial rotator outside of said flow without
substantial interference with flow efficiency.
74. A method of providing improved flow from a valve as described
in claim 73 further comprising interfering with less than 20% of a
flow efficiency through said flow path by said axial rotator.
75. A method of providing improved flow from a valve as described
in claim 73 wherein controlling said flow further comprises flowing
through an eccentric split venturi.
76. A method of providing improved flow from a valve as described
in claim 75 wherein flowing through said eccentric split venturi
comprises flowing through a semicircular eccentric split
venturi.
77. A method of providing improved flow from a valve as described
in claim 73 wherein axially rotating said rotated portion of said
split venturi comprises axially rotating to align with the other
said portion of said split venturi for full flow.
78. A method of providing improved flow from a valve as described
in claim 73 wherein flowing said fluid through a flow path
comprises flowing with a pressure and velocity and further
comprising: a. gradually reducing said pressure of said fluid while
increasing said velocity of said fluid through said first portion
of said split venturi; b. gradually increasing said pressure of
said fluid while decreasing said velocity of said fluid through
said second portion of said split venturi; and c. avoiding
substantial flow separation of said fluid in at least said second
portion.
79. A method of providing improved flow from a valve as described
in claim 73 further comprising establishing a loss coefficient of 4
or less through said valve.
80. A method of providing improved flow from a valve as described
in claim 73 further comprising sealing at an interface between said
portions comprising: a sealing about a periphery of said interface
between said portions; b. sealing across a diametrical portion of
said interface in the same plane as said sealing about said
periphery.
81. A method of providing improved flow from a valve as described
in claim 73 further comprising exiting one of said portions through
an exit port comprising exiting through an internal elbow to a
valve outlet fluidicly connected to said valve.
82. A method of providing improved flow from a valve as described
in claim 81 further comprising sealing at said exit port between
said internal elbow and said valve outlet.
83. A method of providing improved flow from a valve as described
in claim 73 wherein said flowing through said flow path comprises
flowing through a conduit and further comprising inserting at least
one of said portions as a cartridge assembly in said conduit.
84. A method of providing improved flow from a valve as described
in claim 83 further comprising sealing said cartridge assembly in
said conduit.
85. A method of providing improved flow from a valve as described
in claim 73 further comprising sealing at an interface between said
portions and resisting the freezing of said valve by sealing at
said interface a freeze distance away from freezing conditions.
86. A split venturi valve comprising: a. an axially-rotated valve
having a central axis and a flow path; b. a first and second
portion of a split venturi wherein said portions are fluidicly
connected to said valve; c. an axial rotator outside of said flow
path adapted to rotate at least one of said portions of said split
venturi without substantially engaging said portion within said
flow path.
87. A split venturi valve as described in claim 86 wherein said
axial rotator is located outside of said flow path in a location
that has less than 20% interference with a flow efficiency by said
axial rotator relative to a location inside said flow path.
88. A split venturi valve as described in claim 86 wherein at least
said second portion of said split venturi comprises an eccentric
portion.
89. A split venturi valve as described in claim 86 wherein at least
said second portion of said split venturi comprises a semicircular
eccentric portion.
90. A split venturi valve as described in claim 86 wherein said
first and second portions are adapted to axially align relative to
each other for full flow.
91. A split venturi valve as described in claim 86 wherein at least
said second portion of said valve is adapted to substantially
prevent flow separation throughout said portion beginning at an
interface between said first and second portions.
92. A split venturi valve as described in claim 86 wherein said
valve is adapted to establish a loss coefficient of 4 or less.
93. A split venturi valve as described in claim 86 further
comprising a first seal located between said first and second
portions in a transition flow zone wherein said first seal
comprises an outer periphery seal and a diametrical seal in
substantially the same plane as said outer periphery seal
94. A split venturi valve as described in claim 86 further
comprising an internal elbow fluidicly connected to one of said
portions.
95. A split venturi valve as described in claim 86 further
comprising an exit port connected to said second portion and an
exit port seal at an exit port interface between said exit port and
a valve outlet fluidicly connected to said valve.
96. A split venturi valve as described in claim 86 wherein said
axially-rotated valve further comprises a conduit and further
comprising a cartridge assembly adapted for insertion in said
conduit comprising at least one of said portions.
97. A split venturi valve as described in claim 96 further
comprising a cartridge seal assembly around said cartridge assembly
adapted to seal cartridge assembly in said conduit.
98. A split venturi valve as described in claim 86 wherein said
valve comprises a freeze resistant valve comprising a first seal at
an interface between said first and second portions located a
freeze distance away from freezing conditions.
99. A method of providing improved flow from a valve using a split
venturi comprising: a. flowing a fluid with a pressure and velocity
into an axially-rotated valve having a central axis; b. gradually
reducing said pressure of said fluid while increasing said velocity
of said fluid in a first portion of a split venturi; c. flowing
said fluid into a second portion; d. gradually increasing said
pressure of said fluid while decreasing said velocity of said fluid
in a second portion of a split venturi comprising avoiding flow
separation of said fluid in said second portion; e. axially
rotating at least one of said portions of said split venturi along
a longitudinal axis parallel to said central axis to at least a
partially closed position; f. at least partially restricting said
fluid from flowing through said axially-rotated valve; g. axially
rotating said rotated portion along said longitudinal axis to at
least a partially open position; h. allowing said flowing of said
fluid.
100. A method of providing improved flow from a valve as described
in claim 99 wherein axially rotating at least one of said portions
of said split venturi comprises axially rotating said second
portion.
101. A method of providing improved flow from a valve as described
in claim 99 wherein avoiding flow separation of said fluid in said
second portion comprises providing a streamlined flow slope
surface.
102. A method of providing improved flow from a valve as described
in claim 99 wherein gradually increasing said pressure of said
fluid while decreasing said velocity of said fluid in said second
portion comprises gradually increasing through a slope of
approximately 7-8 degrees in said portion.
103. A method of providing improved flow from a valve as described
in claim 99 further comprising planar sealing between said first
and second portions of said split venturi with an outer periphery
seal and a diametrical seal in substantially the same plane as said
outer periphery seal.
104. A method of providing improved flow from a valve as described
in claim 99 wherein gradually increasing said pressure comprises
gradually increasing in a non-axisymmetric flow path relative to
said central axis.
105. A method of providing improved flow from a valve as described
in claim 104 wherein gradually reducing said pressure comprises
gradually reducing in a non-axisymmetric flow path relative to said
central axis.
106. A method of providing improved flow from a valve as described
in claim 105 wherein non-axisymmetric flow paths comprises
semicircular eccentric non-axisymmetric flow paths.
107. A method of providing improved flow from a valve as described
in claim 99 wherein gradually increasing said pressure comprises
gradually increasing said pressure while maintaining streamlined
flow.
108. A method of providing improved flow from a valve as described
in claim 107 wherein gradually reducing said pressure comprises
gradually reducing said pressure while maintaining streamlined
flow.
109. A method of providing improved flow from a valve as described
in claim 108 wherein gradually reducing said pressure comprises
gradually reducing said pressure while maintaining non cavitation
flow.
110. A method of providing improved flow from a valve as described
in claim 99 wherein gradually reducing said pressure comprises
gradually reducing said pressure while maintaining non cavitation
flow.
111. A method of providing improved flow from a valve as described
in claim 99 further comprising establishing a loss coefficient of 4
or less through said axially-rotated valve.
112. A method of providing improved flow from a valve as described
in claim 99 further comprising at least partially sealing at an
interface between said portions.
113. A method of providing improved flow from a valve as described
in claim 99 further comprising reducing a flow area of said flow
path at an interface between said first and second portions to not
less than approximately 40% relative to said flow area in a full
cross sectional area of said flow path.
114. A method of providing improved flow from a valve as described
in claim 112 wherein sealing at said interface comprises linearly
sealing across a diametrical portion of said interface.
115. A method of providing improved flow from a valve as described
in claim 112 wherein sealing at said interface comprises
curvilinearly sealing across a diametrical portion of said
interface.
116. A method of providing improved flow from a valve as described
in claim 112 wherein sealing with a cross sectional seal area to
maintain a seal against full pressure.
117. A method of providing improved flow from a valve as described
in claim 99 further comprising flowing through a longer flow path
in said second portion than said first portion.
118. A method of providing improved flow from a valve as described
in claim 99 further comprising flowing through an interface between
said first and second portion wherein said first and second
portions at said interface comprises an approximately zero
slope.
119. A method of providing improved flow from a valve as described
in claim 99 wherein rotating at least one of said portions
comprises axially rotating said portion with an axial rotator
outside of said flow path without substantial interference with
flow efficiency.
120. A method of providing improved flow from a valve as described
in claim 99 wherein rotating said second portion comprises axially
rotating said portion with an axial rotator outside of said flow
path without substantial interference with flow efficiency.
121. A split venturi valve comprising: a. an axially rotated valve
having a central axis and a flow path; b. a first portion of a
split venturi having a first longitudinal axis parallel to said
central axis; c. a second portion of a split venturi fluidicly
connected to said first portion and having a second longitudinal
axis parallel to said central axis; d. a valve rotator attached to
at least one of said portions of said split venturi wherein said
second portion of said split venturi is adapted to substantially
prevent flow separation throughout said second portion of said
valve beginning at an interface between said first and second
portions.
122. A split venturi valve as described in claim 121 wherein said
valve rotator is adapted to axially rotate at least one of said
portions along said longitudinal axis of said portion.
123. A split venturi valve as described in claim 121 wherein said
second portion of said split venturi that is adapted to
substantially prevent flow separation throughout said second
portion of said valve comprises a streamlined flow slope
surface.
124. A split venturi valve as described in claim 121 wherein said
second portion of said split venturi comprises a slope of
approximately 7-8 degrees.
125. A split venturi valve as described in claim 121 further
comprising a seal located between said first and second portions of
said split venturi and substantially transverse to said central
axis wherein said seal comprises an outer periphery seal and a
diametrical seal in substantially the same plane as said outer
periphery seal.
126. A split venturi valve as described in claim 121 wherein said
flow path through said second portion comprises a non-axisymmetric
flow path relative to said central axis.
127. A split venturi valve as described in claim 126 wherein said
flow path through said first portion comprises a non-axisymmetric
flow path relative to said central axis.
128. A split venturi valve as described in claim 127 wherein
non-axisymmetric flow paths comprises semicircular eccentric
non-axisymmetric flow paths.
129. A split venturi valve as described in claim 121 wherein said
first portion of said split venturi is adapted to substantially
prevent flow separation throughout said first portion of said
valve.
130. A split venturi valve as described in claim 121 wherein at
least one of said portions is adapted to substantially prevent
cavitation throughout said portion beginning at an interface
between said first and second portions.
131. A split venturi valve as described in claim 126 wherein at
least one of said portions is adapted to substantially prevent
cavitation throughout said portion beginning at an interface
between said first and second portions.
132. A split venturi valve as described in claim 121 wherein said
portions are to establish an overall loss coefficient of 4 or
less.
133. A split venturi valve as described in claim 121 further
comprising a first seal at an interface between said first and
second portions.
134. A split venturi valve as described in claim 121 wherein said
flow path comprises a flow area and wherein said flow area at an
interface between said first and second portions further comprises
a flow area not less than approximately 40% relative to said flow
area in a full cross sectional area of said flow path.
135. A split venturi valve as described in claim 133 wherein said
first seal comprises a linear diametrical seal across said
interface.
136. A split venturi valve as described in claim 133 wherein said
first seal comprises a curvilinear diametrical seal across said
interface.
137. A split venturi valve as described in claim 133 further
comprising a cross sectional seal area to maintain a seal against
full pressure.
138. A split venturi valve as described in claim 121 wherein said
second portion has a longer flow path than said first portion.
139. A split venturi valve as described in claim 121 further
comprising an interface between said first and second portions
wherein a slope of said first and second portions approximates zero
at said interface.
140. A split venturi valve as described in claim 121 wherein said
valve rotator further comprises an axial rotator outside of said
flow path adapted to rotate at least one of said portions without
substantial engagement of said portion within said flow path.
141. A split venturi valve as described in claim 121 wherein said
valve rotator further comprises an axial rotator outside of said
flow path adapted to rotate said second portion relative to said
first portion without substantial engagement of said second portion
within said flow path.
142. A split venturi valve as described in claim 121 further
comprising a purge port assembly adapted to open and allow drainage
of said valve when said valve is in at least a partially closed
position.
Description
[0001] This patent is a continuation-in-part of U.S. application
Ser. No. 08/637,203 by Robert K. Burgess, commonly owned by the
Assignee, and filed Apr. 24, 1996, now U.S. Pat. No. ______,
entitled "AXIAL-MOUNTED HIGH FLOW VALVE".
I. FIELD OF INVENTION
[0002] The present invention relates to an improved flow rate valve
system and valve, especially for axially-rotated valves and
includes both apparatus and methods. In particular, the present
invention has applicability where a freeze resistant valve is
preferred.
II. BACKGROUND OF THE INVENTION
[0003] Valves have been used for many centuries in a variety of
applications. As the technology has progressed, more sophisticated
uses have been found for valves. For instance, various improvements
have been made in methods of actuation of the valve. Some of these
methods include motor driven actuation, solenoid actuation and more
recently, computer controlled actuation, and so forth. However, the
essential flow design of valves has stayed relatively constant
along four basic designs.
[0004] One type of valve used is a gate valve. It is simple in
design, inexpensive, and can be used in a variety of applications.
A gate valve typically contains a circular disk, known as a gate,
mounted transverse to a conduit or pipe which engages a seat to
block or restrict flow. A gate valve is generally known to those in
the art as being poor for controlling flow other than in a
fully-opened or fully-closed position. The interface between the
gate and its seat generally erodes and is prone to maintenance.
[0005] Another typical valve is known as a globe valve. Those in
the art know that it is good for throttling at other than
fully-opened or fully-closed positions. An example is shown in U.S.
Pat. No. 4,066,090 to Nakajima et al. As can be seen, the flow path
is somewhat circuitous resulting in generally higher friction
losses, nonlaminar flow, and may prematurely induce flow separation
and/or cavitation. Thus, flow rates tend to be less than those of a
fully-opened gate valve, the fluid flow path tends to wear, and the
globe valve, because of its inherent construction, tends to be
bulky.
[0006] A third type is a ball valve. The ball valve may offer some
advantages of increased flow over the globe valve. The valve
actuator connected to the ball is mounted transverse to the flow.
As the valve opens, the ball is rotated and aligns a central hole
in the ball to the conduit through the valve. The ball valve tends
to be somewhat bulky, generally uses two seating surfaces on either
side of the ball, and may be somewhat expensive to manufacture.
[0007] A fourth type of valve is known as a butterfly valve. The
butterfly valve has an internal seat that is typically oriented
transverse to the conduit. An external valve stem rotates typically
a circular disk transverse to the conduit to engage the seat to
block fluid flow. A butterfly valve generally has high flow rates
and low maintenance. However, it retains the typical construction
of a transverse-mounted valve with a transverse valve stem. While
the valve stem may be remotely actuated by motors and other devices
known to those in the art, it may not be suitable for sealed
installations where it might be desirable to completely encase the
valve, remote actuator, and seat in a conduit for efficient
installation nor is it suitable for installing in a wall structure
where access to the actuator is restricted because of the
transverse orientation.
[0008] An underlying quest in the various designs of valves is a
balance between low friction losses, high flow rates, and
throttling characteristics. Other considerations may include freeze
resistance, simplicity of construction, cost of manufacturing, and
perhaps other specialized uses. While there have been numerous
variations of the valve types such as described above, there
remains a need to provide an improved flow, low friction valve.
This may be especially useful in applications where a remote
actuation along a central axis is desired. Typically, these
installations involve freeze resistant installations.
[0009] In addressing freeze prevention or reduction, efforts have
been concentrated on a remote location of a plug of a globe valve
away from ambient conditions that could lead to freezing. A typical
example is seen in FIG. 7 of U.S. Pat. No. 4,532,954. By remotely
locating the plug, the flow of the liquid, typically water, could
be stopped a distance in a pipe or a conduit away from the freezing
ambient conditions. Those in the art typically concentrated on a
globe valve type seat because of the inherent difficulty of
actuating a gate valve from within the conduit. In this
construction, the nose portion engages a valve seat to seal any
flow at a remote location from adverse ambient conditions. As is
shown in that figure, the nose must engage a valve seat through the
aperture that restricts the flow of water. This remote location
results in a beneficial blocking of the water away from the
freezing ambient conditions. However, it causes other problems. The
wear surfaces may be prone to water erosion and deposits from water
impurities. Also, in order to obtain a proper seal, the mechanical
advantage of the screw of the valve stem may, after much use, crush
the tip of the nose portion. Once the nose was crushed or deformed,
it required even harder tightening of the nose which eventually
lead to leaking (the famous "drip drip"). Also, the inherent design
of the nose portion, engaging an aperture, causes a significant
pressure drop, as those with ordinary skill in the art would
immediately recognize. This significant pressure drop reduces flow
rates. Reduced flow rates may cause a necessarily proportional
increase in the size of conduit, valve, or other devices to obtain
the needed flow rates. Additionally, the use of the nose section
was a modification of the globe valve type seat which required many
turns to suitably seal the flow. Likewise, the valve control rod
(stem) moved in the typical longitudinal direction--it was not
fixed with respect to the conduit or pipe in which it was
assembled. Therefore, increased wear and increased maintenance
resulted from not only the rotational movement, but the
longitudinal movement as it engaged those portions of the valve
seat. While an increase in size of the typical valve might achieve
the necessary flow rates, typically, this was not a viable option
because of size, costs, and compatibility with other components of
the piping system.
[0010] Thus, prior attempts to remotely seal the water flow or
other liquids lead to high pressure drops, low flow rates, and
maintenance. The flow rate is especially important in designing
sprinkling systems. Both residential and commercial sprinkler
systems require a higher flow rate than the typical gate valve or
globe valve delivers for given typical size. Thus, an installation
was not able to use the typical valving of a typical freeze
resistant hydrant--instead, it required a direct connection to
other piping with sophisticated valving controls. The sophisticated
valving, as those with knowledge of sprinkler systems would
recognize, required expensive controls, maintenance, purging during
off-season uses, local and national codes, and other issues.
[0011] A further complication resulted from the axially rotated
valves such as the valves referenced above and others such as U.S.
Pat. No. 3,848,806 to Samuelsen, et al. This actuation shows that
the valve stem on such axially-rotated valves has been heretofore
in the flow path. Until the present invention, on such
axially-rotated valves, it may have been considered by those in the
art that the valve stem was required to be placed in the flow path
in order to engage remotely the nose portion to the aperture.
However, the additional turbulence and volume contained by the
valve stem in the flow path results in additional loss of
efficiency, increased resistance and friction, and lower flow
rates.
[0012] Thus, as systems have become more sophisticated, a need
exists for a valve that can be remotely actuated through the
internal structure of a valve away from adverse ambient conditions,
and yet be inexpensive, easily installed, of the same or similar
diameter to existing piping systems, and still maintain high flow
rates and low pressure drops. If a system was available that would
allow a high flow rate water hydrant that could be converted to a
combination system and water hydrant, it would have an advantage in
the market. It would be advantageous to the dwelling owner in a
reduction of cost, and it would be advantageous to the builder or
installer to simply meet the building requirements of installing
outside faucets and yet allow conversion to sprinkler systems at
minimal costs.
[0013] A significant improvement over the typical valves was
attained in the U.S. application Ser. No. 08/637,203, now issued as
U.S. Pat. No. ______ to Robert K Burgess and upon which this patent
claims a priority date. In that patent, it was realized that a
fixed longitudinal position with axial rotation could establish
high flows and less pressure drop and friction loss and perhaps
less maintenance and less costly installations because of its
compactness. In that patent, the invention provided a specially
designed valve that had a rotatable sealing element longitudinally
fixed in position in a conduit which engaged a seating element
likewise longitudinally fixed in position in the conduit. The
position could be located a sufficient length or distance from for
instance, adverse ambient conditions to enable a sealing of flow
away from the adverse conditions. That valve significantly improved
the flow rates compared to the state of the art known at that time.
Test results suggest that the globe valve might have up to
approximately 2 times the pressure loss for a given flow rate than
the Burgess invention. Similarly, the Burgess invention appears to
have about five times less friction loss than the design shown in
the '954 reference above. This invention also allowed a quarter
turn from a fully-opened to a fully-closed position. Because of its
increased flow, it was felt that it would provide a valve of
suitable flow rates that could be installed in the same size as a
typical conduit and yet meet even the more demanding sprinkler
systems requirements. Among other things, however, that valve
retained the typical valve stem located in the flow path.
[0014] As an example of the significant improvement in pressure
drop by the present invention, FIG. 1a shows the pressure drop as a
function of flow rate for various commercially available
axially-rotated freeze resistant valves. FIG. 1b shows a graph of
measured loss coefficients as a function of Reynolds number for the
present invention compared to some commercially available
axially-rotated valves and other types of valves, again to show
some of the significant improvements of the present invention. The
two top curves show valves by competitors, such as are designed for
higher flow rates on sprinkler feed systems. Although the '203
valve appeared to have significant improvement over technology
existing at the time, the present invention shows an even greater
flow rate for a given pressure drop or conversely a lower pressure
drop at a given flow rate. The present invention may have a 4 times
improvement over some of the competition when based on pressure
drops at a given flow rate.
[0015] Another reference, U.S. Pat. No. 286,508 to Vadersen, et
al., shows an early attempt in providing an axially-rotated freeze
resistant valve. For some reason, the embodiment apparently was not
received commercially. Perhaps, two reasons exist. First, the valve
plate (G) with apertures (H), when aligned with valve (K) in
apertures (T), as those with ordinary skill in the art would
readily recognize, would create nonlaminar flow, increased friction
loss, flow separation, and perhaps cavitation (depending on the
vapor pressure of the fluid at that temperature). Secondly, the
valve stem appears located in the flow path. This is in direct
contrast to the present invention which in some embodiments uses an
axially-rotated split venturi to avoid the problems of the Vadersen
reference. Thus, it may be that from the Vadersen reference to the
present invention of 114 years, little improvements along this
particular line appear to have been thought appropriate.
[0016] The present invention goes beyond the inventions of the
earlier valves and even the U.S. application Ser. No. 08/637,203.
The present invention improves the flow rates for a given supply
pressure several times over the '203 invention. It has a loss
coefficient lower than any known axially rotated valve. Its loss
coefficient has been tested and may be approximately 50% of a
typical axially rotated valve. It may be even simpler to construct,
typically avoids the valve stem in the flow path, offers good
throttling characteristics, and yet retains higher flow rates for
given pressure drops.
[0017] Thus, there has been a long felt, but unsatisfied need for
the invention that would meet and solve the problems discussed
above. The present invention represents the next step in the quest
for low friction, high flow and good throttling characteristics,
especially in applications where remote actuation of
axially-rotated valves is desired. While implementing elements have
all been available, the direction of the inventions of other
persons have been away from the present invention. The efforts have
primarily concentrated on longitudinally moving backward or forward
a nose or other sealing element against a valve seat, typically
including an aperture. This has resulted in the above-discussed
problems, such as poor flow rates. Those in the art appreciated
that a problem existed and attempted to solve the problem with
technology as shown in Pat. No. 4,532,954. Even with the
improvements of the invention of U.S. Ser. No. '203, the problem
still existed at less than optimal flow rates for given pressure
drops. Alternatively, those in the art simply accepted the extra
expense of extra installations, complicated valving, and other
requirements necessary for such applications as sprinkler systems.
This general mind set taught away from the technical direction that
the present invention addresses. It might be unexpected that a
valve can have significantly higher flow rates and yet remotely
control or block the fluid flow with the same or similar size
conduit or pipe found in a typical installation and still offer an
economical solution. Until the present invention, it appears that
those skilled in the art had not contemplated the solution offered
by the present invention.
III. SUMMARY OF THE INVENTION
[0018] A primary goal of the present invention is to provide a
design which permits increased flow rates for axially-rotated
valves, especially those used in freeze resistant prevention valves
and sprinkler systems. By recognizing and utilizing the advantages
of a wholly different layout and design of a valve, this valve
achieves its goals.
[0019] The present invention provides an axially-rotated valve
which permits increased flow rates and lower pressure drop by using
an axial eccentric split venturi with two portions where at least
one portion is rotatable with respect to the other portion. (As
would be known to those with ordinary skill in the art, a typical
venturi is a conical contraction then expansion of a conduit
through which a fluid flow. Venturies typically are high efficiency
devices primarily used for measuring the flow rates of fluids, see
e.g., Beckwith, Thomas, Marangoni, Roy, Lienhard V, John,
Mechanical Measurements p. 617 (Addison-Wesley Publ. Co. 5th ed.
1993)). The axially-rotated valve typically may be designed to
avoid flow separation and/or cavitation at full flow under a
variety of conditions. The valve may be designed, in some
embodiments, to delay a transition from laminar flow in at least
some portion of the split venturi. A typical cross section of the
eccentric split venturi may be non-axisymmetric such as a
semicircular cross section which may assist in both throttling
capabilities and in maximum flow capacity using the design of the
present invention. Such a design can include applications for
freeze resistant axially-rotated valves and may be fully-opened and
fully-closed in one-half of a complete rotation. An internal elbow
typically connected to a rotatable portion of the eccentric venturi
may assist in directing flow with lower friction losses and
pressure drop. A valve actuator may actuate in an axial manner yet
be uniquely located outside of the axial flow path to further
reduce friction losses. A seal may be used between the two portions
that may include a peripheral and diametrical seal in the same
plane.
[0020] Typically, the present invention may be envisioned as useful
on residential and commercial installations where it would be
desirable to economically reduce the possibility of freezing of the
valve. Such applications could also involve sprinkler systems, both
underground and above ground. Rather than supplying a system which
affords only an incremental increase in performance and design over
prior art, the present invention utilizes a technique to achieve
significant performance improvement compared to past efforts. The
valve of the present invention satisfies one of the criteria by
being inexpensive to manufacture and yet offers high flow rates,
good maintenance, low pressure drop, and throttling
capabilities.
[0021] This invention has a significant advantage in the sizing of
valves and pipes. It retains the desirability of quickly opening
and closing from a fully-opened to a fully-closed position. At a
fill flow, in some embodiments, the present invention seeks to
sustain a streamlined, noncavitating flow, and in some embodiments,
a somewhat laminar flow. This may result in less turbulence and
reduced friction loss. This invention is particularly important in
resolving the difficulties with axially-rotated valves mounted in
the flow stream and actuated along a longitudinal axis parallel to
a central axis of the valve in a flow direction.
[0022] Another goal of the present invention is to provide a design
for an axially-rotated valve which permits increased flow rates and
less pressure drop using an axial eccentric split venturi with two
portions where at least one portion is rotatable with respect to
the other portion. An objective of this goal is to provide an axial
rotator to rotate at least one of the portions without a
substantial engagement of the axial rotator within the flow path.
Another goal is to provide an eccentric split venturi approximating
the shape of a semicircular cross section in a direction transverse
to the flow path which may assist in both throttling capabilities
and in maximum flow capacity with the design of the present
invention. Such a design can include the object of providing a
freeze resistant axially-rotated valve. It may be provided with a
length of at least six inside diameters (preferably seven or eight)
of the portion, particularly the downstream portion, to assist in
providing smooth transitional flow through the split venturi.
Another objective may be to provide a cartridge assembly comprising
at least part of the valve so that it may be easily retracted and
inserted into a conduit of the valve. Such a design may be
fully-opened and fully-closed in one-half complete rotation. While
this may not be as rapidly opening as the embodiment shown in the
'203 invention, it is believed that such a rapid rotation will
satisfy the goals and objectives of the marketplace. Also, the
invention may include a purge port adapted to open and allow
drainage of the valve when the valve is in at least a partially
closed position and typically in a fully-closed position. By using
a split venturi, the flow rate on the inlet side of the split
venturi would include gradually reducing the pressure of the flow
as it flows into the first portion of the split venturi and at the
same time increasing the velocity of the flow. At the split or
interface of the split venturi between the first portion and a
second portion, the flow would start to gradually increase in
pressure while decreasing in velocity as it flows through the
second portion of the split venturi to some exit port. In some
instances, the ambient conditions may be such that the conduit
itself may provide a conduction path to adverse ambient conditions,
such as freezing temperatures. In such instances, it may be
beneficial to split the conduit in the freezing area and create a
thermal barrier between at least the two portions of the conduit
such that the energy is not lost to adverse ambient temperatures.
At the interface behind the first portion and second portion, a
seal may be used. Such a seal could be adapted to seal the
periphery of the interface and in some instances seal
diametrically, as will be discussed further. The diametrical seal
may be linear or, in some fashion, curvilinear. In some
embodiments, the conduit might not be rigid, at least in parts. The
conduit might include for instance a flexible tube. A proper
location might be such that no interference of the seal between the
first and second portions might occur.
[0023] Another goal of the present invention is to provide a valve
that includes a split venturi between the first and second portion
where the portions are non-axisymmetric relative to a central axis.
Heretofore, the typical venturi design has been concentric in that
at any given cross section the outer periphery is equidistant from
a central axis. The present invention abruptly departs from this
standard practice by having a non-axisymmetric or eccentric venturi
that is split in two sections. The two sections may be fluidly
connected to one another such as the fluid might flow from one into
the other with little change across the interface. Furthermore,
such a flow path may be semicircular. By departing from this
standard practice of axisymmetric venturis, the present invention
is better able to utilize its unique closing and opening
capabilities. It is another objective of the present invention to
include a rotating internal elbow connected to at least one of the
portions that rotates so that as the portion is rotated, the
internal elbow can direct the flow into a valve outlet.
[0024] Another goal of the present invention is to include an
axially-rotated valve using a split venturi having a first and
second portion where at least one portion may be rotated by an
axial rotator outside of the flow without substantial interference
with flow efficiency. One objective of this goal is to provide an
axially-rotated valve that is designed to provide streamlined flow
(that is, avoiding flow separation and/or cavitation at full flow
under a variety of conditions).
[0025] Naturally, other objectives of the invention are disclosed
throughout other areas of the specification and claims. In
addition, the goals and objectives may apply either in dependent or
independent fashion to a variety of other goals and objectives in a
variety of embodiments.
IV. BRIEF DESCRIPTION OF THE DRAWINGS
[0026] FIG. 1a shows a graph of pressure drop as a function of flow
rate test results of the present invention compared to some
commercially available axially-rotated valves to show some of the
significant improvements.
[0027] FIG. 1b shows a graph of measured loss coefficients as a
function of Reynolds number for the present invention compared to
some commercially available axially-rotated valves and other types
of valves, again to show some of the significant improvements of
the present invention.
[0028] FIG. 2 is a cross section of the present invention from a
side perspective in a fully-opened orientation.
[0029] FIG. 3 is a cross section of the present invention from a
side perspective in a fully-closed orientation.
[0030] FIG. 4 shows an end view of the first portion (8) in a
non-axisymmetric eccentric embodiment shown in FIG. 3.
[0031] FIG. 5 shows an end view of the second portion (18) in a
non-axisymmetric eccentric embodiment shown in FIG. 3.
[0032] FIG. 6 is an end view of a seal at an interface between a
first and second portion.
[0033] FIG. 7 is an end view of a seal at an interface between a
first and second portion as an alternative embodiment to FIG.
6.
V. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
[0034] As mentioned earlier, the present invention includes a
variety of components that may be used in various combinations,
depending on the application that needs to be addressed. This
invention is intended to encompass a wide variety of embodiments of
an axially-rotated valve. In particular, the invention is designed
primarily to take advantage of low friction loss, high efficiency,
high flow through an eccentric split venturi of a particular and
novel design and combine and modify as needed for a variety of
shapes, sizes and orientations, as will be explained in more detail
as the figures are described. Elements, functions and procedures
that distinguish the present invention will be noted where
appropriate.
[0035] As can be easily understood, the basic concepts of the
present invention may be embodied in a variety of ways. It involves
both methods and devices to accomplish the appropriate method. In
this patent, the methods are disclosed as part of the results shown
to be achieved by the various devices described and as steps that
are inherent to utilization. They are simply the natural result of
utilizing the devices as intended and described. In addition, while
some devices are disclosed, it would be understood that these not
only accomplish certain methods, but also can be varied in many
ways. Importantly, as to the foregoing, all these facets should be
understood to be encompassed by this disclosure.
[0036] FIG. 2 shows a fully-opened eccentric split venturi
axially-rotated valve in a cross-section side view. Starting from
the left of the valve (2), a flow (4) enters the valve. The valve
may have a central axis (6) which for a typical valve may operate
as a center line of the valve. As the flow (4) enters the valve
(2), the flow may first encounter a first portion (8) having a
first longitudinal axis (10) and a first flow path (12). The flow
(4) may progress across an interface (14) along a first flow axis
(11) in a transition flow zone (16) and into a second portion (18).
The second portion (18) may have its own second flow axis (21), a
second longitudinal axis (20), a second flow path (22), and a
diameter (24). As the flow continues, it may exit through an exit
port (26). The exit port in some embodiments may include an
internal elbow (28) to help direct the flow (4) into a valve outlet
(30).
[0037] The first portion (8) may be a fixed sleeve inside the valve
(2). By fixed, it is intended to mean that generally the first
portion remains in a constant rotational orientation with respect
to the valve in use. The first portion (8) may be removable from
the valve or may be more securely attached, such as being made
integral to the valve, welding, brazing, adhesively attaching,
compression fitting, and so forth as would be known to those
skilled in the art. One possibility for the first portion (8) is
that it may be a cartridge assembly which may be removable for
maintenance or replacement purposes. As a cartridge assembly, it
may include cartridge seals (32) in a variety of places as would be
appropriate and known to those skilled in the art.
[0038] The first portion (8) may include an eccentric portion of a
split venturi. A typical venturi includes a smooth transition from
a large diameter to a small diameter and then again to a large
diameter. The present valve uniquely uses a venturi that is split
into at least two portions. At the split, the interface (14)
results in a transition flow zone (16) from a decreasing cross
sectional area to an increasing cross sectional area. The first
portion (8), working in conjunction with the second portion (18),
to be described in more detail below, typically would have an
eccentric split venturi so that by rotating the second portion, a
closure of the flow (4) may be had.
[0039] As the flow (4) continues along the first portion (8) and
engages the split venturi (34), it encounters an inlet slope (36).
The inlet slope (36) may form a conical shape of uniform slope
about the periphery of the flow path with respect to the
longitudinal axis in some embodiments. However, in the preferred
embodiment, the slope may form an eccentric slope. By eccentric, it
is meant to relate to a slope along a longitudinal perspective and
may include such slopes as are shown in FIG. 2 where the flow-path
may have different slopes about the periphery of the flow path.
This would include diverging the center of the flow (4) from the
longitudinal axis (10) to the first flow axis (11). Similarly, an
eccentric slope could diverge the flow path through second portion
(18) along a central second flow axis (21) then to second
longitudinal axis (20). The first flow axis (11) and second flow
axis (21) are central axes of the flow paths through the first
portion (8) and second portion (18) and may vary in relative height
with respect to the central axis (6) as the flow turns up the first
slope (36) and into the split venturi (34) and then down slope
(40). (The first longitudinal axis (10) and the second longitudinal
axis (20) in the preferred embodiment may coincide with the central
axis (6) through the valve.) As the flow continues toward the
transition flow zone (16), the slope may decrease. In the preferred
embodiment, the slope may be a zero slope, that is, neither
decreasing nor increasing in cross sectional area at the interface
(14) in the transition flow zone (16). In the preferred embodiment,
the slope on the first portion (8) appears to be less critical than
the slope on the second portion (18). Thus, the slopes may be
different. The slope on the first portion may be approximately 5-15
degrees, although other angles could be suitable, and for some
embodiments a slope of 9-11 degrees may be appropriate.
[0040] In addition to the eccentricity of the split venturi, the
cross sectional area across the flow path shown more accurately in
FIG. 3 may be non-axisymmetric, such as approximately semicircular.
By semicircular, it is not meant to be restricted to an exact
180.degree. of a perfect circle; it can have a variety of shapes
that could include approximately one-half of a flow area of the
flow path of the flow (4) less any requirements for a diametrical
seal such is shown in FIGS. 6 and 7. The non-axisymmetric aspect of
FIG. 4 relates to the cross sectional flow area. For instance, the
first flow axis (11) is shown at a center of the cross sectional
area, where the center represents a midpoint of the distances to
the periphery. In other words, the points of the periphery of the
flow area are not equidistant from the first flow axis (11).
Similarly, in FIG. 5, the second portion (18) may have a
correspondingly shaped cross sectional flow area about a second
flow axis (21) to align with the cross sectional area and flow path
with the first portion (8).
[0041] Returning to FIG. 2, as the flow flows across the interface
(14) in the transition flow zone (16), the flow enters the second
portion (18). As would be known to those skilled in the art, in the
transition flow zone, the pressure exerted by the flow may be
minimal due to the characteristics of the split venturi. However in
a closed position (shown in more detail in FIG. 3), the static
pressure of the substance such as a fluid may exert pressure at the
interface (14) between the first portion (8) and the second portion
(18). If desired, a first seal (38) may be provided in the
interface (14).
[0042] As a flow flows through the second portion (18), the flow is
gradually increased in pressure and decreased in velocity. Test
results show that for optimal flow characteristics, and in order to
obtain less friction loss and higher flow rates, the slope (40) of
the second portion (18) may be more important than the first slope
(36). The slope (40) may be inclined at an angle of approximately
5-15 degrees, and in the preferred embodiment, approximately 7-8
degrees. The length to diameter ratio may be at least 6:1, and
preferably at least 8:1. In other words, the length of the second
portion (18) in the preferred embodiment may be at least six times
longer than the diameter (24) of the second portion (18) for
optimal flow characteristics in reducing pressure drop and
increasing flow rate for a given pressure and diameter. It has been
observed that such a slope may avoid, under many conditions, the
flow separation and/or cavitation of the fluid as it flows from the
first portion into the second portion and through the second
portion. Cavitation and flow separation will be discussed in more
detail below.
[0043] At some point along the second portion (18), the flow (4)
may exit through an exit port (26). To assist in reducing the
pressure drop from the flow, a smooth transition may be preferable.
A smooth transition in exit port (26) may include an internal elbow
(28). The internal elbow may be fluidicly connected or may be
integral to the second portion (18). In some embodiments, the
integral elbow may be fluidicly connected to the first portion (8).
As the flow exits through the exit port and perhaps through the
internal elbow (28), the flow may be directed through a valve
outlet (30). In some embodiments, it may be useful to have an exit
port seal (42) located at the exit port interface (44) between the
exit port (26) and valve outlet (30). This exit port seal (42)
might further enhance any sealing capabilities such as might be
needed for a particular application. The valve outlet (30) could
include typical hose connections, hose bibs, and so forth as would
have commonly known to those in the industry. To further assist the
flow out of the exit port region and through the valve outlet, the
internal elbow may be configured (such as be casting, molding,
machining, and so forth) to a more circular shape (from the
preferred embodiment's semicircular cross section) so that the flow
may proceed into the typically circular valve outlet shape such as
a hose bibb, known to those in the art.
[0044] In the preferred embodiment, a valve actuator (48) may act
in an axial direction to rotate the second portion (18) where the
second portion (18) could be described as a rotatable sleeve. As
discussed earlier, one of the pressure losses (up to approximately
20% of the pressure loss) of axially-rotated valves has included
the presence of a valve stem within the flow path. As can be seen
in FIG. 2, the valve actuator (48), operating in an axial fashion,
is outside the flow path. The valve actuator in FIG. 2 may be
directly connected and may be integral to the rotatable sleeve
functioning as a second portion (18). Thus, the valve actuator (48)
may cause no or little pressure loss compared to a valve actuator
located within the flow path of the flow (4) of typical axially
rotated valves such as disclosed in U.S. Pat. No. 4,532,954. To
operate the valve, the valve actuator might only be turned
approximately one-half turn from a filly-opened to a fully-closed
position. As would be known to those skilled in the art, a packing
or other sealing member (46) could be used to seal the valve from
internal leakage along the area of the valve actuator (48).
[0045] Similar to the first portion (8) being included as a
cartridge, the second portion (18) may similarly be included as a
cartridge. This could be especially suitable if the first portion
(8) were fixed in position in a more permanent mode. Thus if
replacement and maintenance were desired, the cartridge assembly
could include the valve actuator, internal elbow, exit port and
other parts of the second portion (18) and perhaps even the first
seal (38) so that quick and easy maintenance could be
accomplished.
[0046] To aid in the sealing of the second portion (18) with the
first portion (8), an axial compression member (50) may be
included. For instance, in the preferred embodiment, the axial
compression member (50) may be a spring or a Bellville washer, as
would be known to those with skill in the art, or other biasing
elements.
[0047] A further aspect of the present invention may include the
provision of a purge valve (52). The purge valve (52) may include a
purge plug (54), a purge biasing member (56), and a purge seat
(58). A purge valve actuator (60), for instance, located on a
second portion (18), when rotated to an appropriate position, could
push the purge plug (54) against the purge seat (58) and seal the
purge port when a flow condition existed. When a purge valve
actuator was rotated to an offset position, the purge biasing
member (56) could bias the purge plug (54) off the purge seat (58)
and allow drainage of any appropriate spaces.
[0048] In some instances in adverse ambient conditions, such as
freezing weather, it may be preferable to provide a thermal break
in the conduit. The conduit (62) may be an external portion of the
valve body. Typically, this may include some metallic substance
such as brass, steel, copper, bronze, and so forth as would be
known to those skilled in the art. Because metal typically is a
conductor, as opposed to an insulator, the exposure of the conduit
surfaces to adverse ambient conditions may encourage freezing at
the valve. In such instances, it may be preferable to provide a
thermal break (64) and divide the conduit into at least a first
conduit section (66) and a second conduit section (68). The thermal
break may include a variety of substances such as nonconductive
plastic, insulation, or any other elements such as would retard the
adverse ambient condition from being transmitted down the conduit.
One of the aspects of the present valve is that it may allow the
location of the thermal break in a variety of locations.
[0049] FIG. 3 shows the valve in a fully-closed position. The first
portion (8) has remained in position; however, the second portion
(18) has been rotated, in this instance, approximately 180.degree.
about its longitudinal axis. In the preferred embodiment, the
longitudinal axis overlaps the central axis (6). However, it is
possible that other embodiments could vary the alignment. It is
envisioned that in most instances, the longitudinal axis will at
least be substantially parallel to the central axis (6). By
parallel, it is meant to include unless otherwise stated
substantially parallel up to an approximately 30.degree.
deviation.
[0050] As can be shown in FIG. 3, the internal elbow may be rotated
into a nonaligned position with respect to the valve outlet (30).
As described in FIG. 2, there may be a seal between the internal
elbow (28) at the exit port interface (44) and the valve outlet
(30). Thus, it might even be, in some embodiments, that the first
seal (38) might not be present. Also, as shown in FIG. 3, the valve
actuator (48) has simply been rotated approximately 180.degree. or
a one-half turn rotation to effect the restriction of the flow (4).
Such a quick shut off or restriction may be useful in many
instances. Also shown in FIG. 3 is the purge valve actuator (60) in
a rotated position away from the purge valve (52) where the purge
plug (54) has been biased away from the purge seat (58).
[0051] As mentioned earlier, FIG. 2 and FIG. 3 show a first seal
(38). FIGS. 3, 6, and 7 show the peripheral seal (70) and the
diametrical seal (72) (as a linear diametrical seal (76) and a
curvilinear diametrical seal (82)). As the second portion (18) and
first portion (8) are biased toward each other, the first seal (38)
acting through the peripheral seal (70) and the diametrical seal
(72) may restrict leakage of the flow (4) from the first portion
(8) into the second portion (18). It may also restrict leakage into
the cavity (74) between the conduit (62) and the first and second
portions.
[0052] This term seal is intended as a functional term. Thus, a
separate member may not be necessary. For instance, some test
results show that some materials may inherently seal without the
necessity of a separate seal. For instance, Delrin.TM. is generally
considered a hard plastic, and yet appears to be soft enough (with
a durometer of approximately 80) such that a seal may be effected
functionally. Such a seal may be enhanced by the axial compression
member (50) pressing the first portion (8) and second portion (18)
toward each other. Another advantage of Delrin.TM. appears to be
that it is a self lubricating plastic. In other words, it may
resist scoring as it is rotated back and forth. Other materials
that may offer possibilities are other polymers, ceramics, various
metals, and so forth. The appropriate material may be varied
depending upon the particular application. For instance, it is
known that softer materials resist erosion of abrasive materials
better than harder materials. Thus, those with a lower durometer,
may be more suitable in some instances, as would be known to those
with skill in the art. Furthermore, while the conduit (62) has been
described generally in a metallic fashion, it is entirely feasible
to have a conduit of other materials such as plastics and so forth.
In some instances, the conduit could even be made of a soft
flexible material, at least in a portion.
[0053] Also, as would be known to those with skill in the art, an
in-line spool perhaps with two seals between the first portion (8)
and the second portion (18) could be useful in some embodiments.
Naturally, other embodiments could be used. In some instances, it
may not even be important to have a seal between the first and
second portion. The market place and commercial concerns might
dictate the particular variations.
[0054] The valve rotator (48) has been shown to be connected to the
second portion (18). Naturally, other embodiments are possible. For
instance, because the flow between the first and second portions
may be sealed from the cavity (74), it is possible that side
mounted valve actuators that might extend through the conduit (62)
could rotate for instance the second portion (18). Such a valve
rotator could still be considered an axial rotator because it could
indeed rotate for instance the second portion (18) along the second
longitudinal axis (20) and even be outside the flow path of the
flow (4).
[0055] FIG. 6 shows an end view of the first seal (38). As
described above, the first seal (38) could functionally be
incorporated into the particular material used as the first portion
(8) or the second portion (18) or both. The first seal (38) might
include a peripheral seal (70). The peripheral seal as shown in
FIGS. 2 and 3 might seal the outer perimeter of the first and
second portions. The first seal (38) might also include a
diametrical seal (72), shown in FIG. 6 more particularly as a
somewhat straight linear diametrical seal (76). As shown in FIG. 2
and FIG. 3, the diametrical seal (72) might be located at the
juncture where the first portion and second portion are rotated
with respect to each other along the respective longitudinal axis.
The thickness and width and resulting cross sectional area of the
diametrical seal might be structured to contain the full pressure
of the flow (4) when the second portion (18) is rotated to a
restricting position, shown in FIG. 3. This typically would relate
to the strength of materials, pressure, diameter, and other factors
known to those with skill in the art. By diametrical, the term is
meant to include a variety of cross sections such as circular,
eccentrical, rectangular, square, and other cross sectional areas.
In the test results, it appears that the flow area (78) of FIG. 4
might correspond to the open area (80) of the seal in FIG. 6 such
that the flow area (78) might not be less than approximately 40% of
the flow path in the preferred embodiment compared to the flow
area, for instance, at the diameter (24). (The various percentages
and members described in this patent are approximate and may be
varied according to the particular conditions and flows desired.)
The linear diametrical seal (76) as shown in FIG. 6 may be
substantially planar to the peripheral seal (70).
[0056] FIG. 7 shows an alternative embodiment of the diametrical
seal (72). While FIG. 6 shows a somewhat straight linear
diametrical seal, the present invention is not so restricted. It
may include a variety of seals in a diametrical fashion. Such a
seal could include the curvilinear diametrical seal (82) shown in
FIG. 7. In most instances, where a high flow was desired, the
minimal restriction would be preferred. Thus, the cross sectional
area of the diametrical seals would preferably be minimized to
effect the higher flow rates.
[0057] It is a goal of the present invention to minimize pressure
drop through the valve, even at high flow rates. Increased pressure
drop may be caused by turbulent flow, flow separation, and/or
cavitation. Flow in piping components, including valves, is
typically characterized by the loss coefficient, which is
proportional to the pressure drop through the component and
inversely proportional to the fluid density and inversely
proportional to the fluid velocity squared. The flow coefficient
may be represented by the formula: K.sub.L=.DELTA.P/1/2.rho.V.sup.2
where K.sub.L represents the flow coefficient, .DELTA.P represents
the pressure drop, .rho. represents the density of the fluid, and V
represents the average velocity of the fluid in the nominal
pipe.
[0058] By manufacturing and using a slope (40) for the eccentric
split venturi such as described above, and even perhaps by using an
internal elbow (28), the loss coefficient can be minimized.
(Obviously, other steps, in addition to and in lieu of, may be
taken that could result in a lower loss coefficient.) This may
result in a valve with a lower pressure drop even at high flow
rates. Test results have shown that the loss coefficient of this
particular invention is less than those of any known
axially-rotated valve. The loss coefficient for this type of valve
may range in the area of 4 or less. (Obviously, this value is
intended to cover ranges of approximately 4 and is not intended to
apply specifically to 4.000. The same is true for the other values
expressed in this application.) For the preferred embodiment, the
range may be 3.5 or less. By comparison, the loss coefficient of
other types of axially-rotated valves such as that disclosed in the
'954 reference described above has been measured to be 15 at
comparable flow conditions. The present invention has even a lower
loss coefficient than other types of axially actuated valves used
in the marketplace. As would be known to those in the art, the loss
coefficient may be fairly constant across a range of flows and,
thus, the improvements of the present invention may apply
broadly.
[0059] Another aspect of the invention relates to flow separation.
Separation may occur when there is flow over or past an
insufficiently streamlined, blunt object. When the flow rate
becomes sufficiently large, the streamlines of the flow past such
objects no longer follow the boundaries of the flow. Indeed, flow
may actually reverse in the separated region, which actually
decreases the effective cross-section area of a closed conduit.
(See, e.g., Munson, Bruce, Young, Donald, Okiishi, Theodore,
Fundamentals of Fluid Mechanics, p. 558 (John Wiley & Sons 2d.
ed. 1994)). Thus, flow separation leads to higher pressure drop,
resulting in an overall higher loss coefficient. This invention has
been designed to minimize or eliminate flow separation.
[0060] It is also a goal of the present invention to include
noncavitational flow in some embodiments. The embodiments
described, especially in FIGS. 2 and 3, may assist in this goal.
Generally, the transition flow zone (16) appears to be the more
important area to assist in avoiding cavitation. The cavitation
occurs, as would be known to those with skill in the art, when the
flow characteristics establish a pressure gradient that exceeds the
vapor pressure for a given fluid at a given temperature. By
manufacturing and using a transition flow zone for the eccentric
split venturi described above, cavitation may be avoided in many
instances at full flow at least in this area of the valve.
Generally, in the preferred embodiment, this area should be as
large as possible in keeping with the goals and objectives of the
present invention to lessen the risk of cavitation, where
appropriate.
[0061] In some embodiments, the flow may also be somewhat laminar.
While there may be boundary layer flow that on a microscopic scale
might not be laminar, as would be known to those with skill in the
art, the laminar flow on a macroscopic scale may be realized to the
present invention. Laminar flow is one in which the fluid flows in
layers. There may be small macroscopic mixing of adjacent fluid
layers. The laminar flow may be seen, for instance, by introducing
a dye somewhere in the stream to develop a stream line which flows
through a portion of the valve without substantial deterioration.
In such instances, the laminar flow may point to the smoothness of
the flow with the resulting lower friction loss and higher flow
rates for a given size of valve at a given pressure. As would be
known to those with skill in the art, the laminar flow
characteristics can be related to the Reynolds Number. Thus, by
choosing an appropriate curve, which may include the type described
for slope (40) above for the eccentric split venturi, the pipe
diameter (that is a cross sectional area at any given point in the
venturi) and the average flow velocity may be carefully controlled
so that an appropriate Reynolds Number may not be exceeded and the
flow is somewhat laminar in some portion of the split venturi and
may include a substantial percentage of the second portion (18).
(The discussion of flow separation, cavitation, and laminar aspects
does not necessarily include the flow through the exit port and
internal elbow.)
[0062] Regarding the throttling characteristics, it may be seen
that as the first portion (8) and second portion (18) are rotated
using, in the preferred embodiment, the semicircular eccentric
split venturi, an unusually small area of the flow path (78) of the
first portion may correspond to an unusually small area of the flow
path of the second portion as the valve is closed. In other words,
a small portion of the diametrical "pie" may be used for small
variations in controlling the flow.
[0063] Each of these valve embodiments could include various facets
of the present invention. Some may include flow separation and/or
cavitation flow avoidance elements, while others may not include
such elements. Some may include varieties of seals and others not
include such seals, while still others may include certain optimal
flow lengths while others may be less concerned about the optimal
flow length. The market place and manufacturing concerns may
dictate the appropriate embodiments for the present invention.
[0064] The foregoing discussion and the claims that follow describe
only the preferred embodiments of the present invention.
Particularly with respect to the claims, it should be understood
that a number of changes may be made without departing from the
essence of the present invention. In this regard, it is intended
that such changes, to the extent that they substantially achieve
the same results in substantially the same way, will still fall
within the scope of the present invention.
[0065] Although the methods related to the system are being
included in various detail, only initial claims directed toward the
valve have been included. Naturally, those claims could have some
application to the various other methods and apparatus claimed
throughout the patent. The disclosure of the apparatus or method
context is sufficient to support the full scope of methods and
apparatus claims with, for instance, the axially-rotated valves,
purge ports, non-axisymmetric venturis, internal elbows,
unseparated, non cavitation, and laminar flow designs, and so
forth. While these may be added to explicitly include such details,
the existing claims may be construed to encompass each of the other
general aspects. Without limitation, the present disclosure should
be construed to encompass subclaims, some of those presented in an
apparatus or method context as described above for each of the
other general aspects. In addition, to the extent any revisions
utilize the essence of the invention, each would naturally fall
within the breadth of protection encompassed by this patent. This
is particularly true for the present invention since its basic
concepts and understandings may be broadly applied.
[0066] As mentioned earlier, this invention can be embodied in a
variety of ways. In addition, each of the various elements of the
invention and claims may also be achieved in a variety of manners.
This disclosure should be understood to encompass each such
variation, be it a variation of an embodiment of any apparatus
embodiment, a method or process embodiment, or even merely a
variation of any element of these. Particularly, it should be
understood that as the disclosure relates to elements of the
invention, the words for each element may be expressed by
equivalent apparatus terms or method terms--even if only the
function or result is the same. Such equivalent, broader, or even
more generic terms should be considered to be encompassed in the
description of each element or action. Such terms can be
substituted where desired to make explicit the implicitly broad
coverage to which this invention is entitled. As but one example,
it should be understood that all action may be expressed as a means
for taking that action or as an element which causes that action.
Similarly, each physical element disclosed should be understood to
encompass a disclosure of the action which that physical element
facilitates. Regarding this last aspect, the disclosure of a "seal"
should be understood to encompass disclosure of the act of
"sealing"--whether explicitly discussed or not--and, conversely,
were there only disclosure of the act of "sealing", such a
disclosure should be understood to encompass disclosure of a
"seal." Such changes and alternative terms are to be understood to
be explicitly included in the description.
[0067] It is simply not practical to describe in the claims all the
possible embodiments to the present invention which may be
accomplished generally in keeping with the goals and objects of the
present invention and this disclosure and which may include
separately or collectively such aspects as axially-rotated valves,
eccentric split venturis, internal elbows, valve actuators located
outside the flow path, and other aspects of the present invention.
While these may be added to explicitly include such details, the
existing claims should be construed to encompass such aspects. To
the extent the methods claimed in the present invention are not
further discussed, they are natural outgrowths of the system or
apparatus claims. Therefore, separate and further discussion of the
methods are deemed unnecessary as they otherwise claim steps that
are implicit in the use and manufacture of the system or the
apparatus claims. Furthermore, the steps are organized in a more
logical fashion; however, other sequences can and do occur.
Therefore, the method claims should not be construed to include
only the order of the sequence and steps presented.
[0068] Furthermore, any references mentioned in the application for
this patent as well as all references listed in any information
disclosure originally filed with the application are hereby
incorporated by reference. However, to the extent statements might
be considered inconsistent with the patenting of this/these
invention(s), such statements are expressly not to be considered as
made by the applicant(s).
* * * * *