CA1077010A - Multi-position disc slide valve - Google Patents
Multi-position disc slide valveInfo
- Publication number
- CA1077010A CA1077010A CA288,687A CA288687A CA1077010A CA 1077010 A CA1077010 A CA 1077010A CA 288687 A CA288687 A CA 288687A CA 1077010 A CA1077010 A CA 1077010A
- Authority
- CA
- Canada
- Prior art keywords
- valve
- orifice plate
- disc
- members
- disc members
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
- F16K3/029—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with two or more gates
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
- F16K3/30—Details
- F16K3/32—Means for additional adjustment of the rate of flow
Abstract
ABSTRACT OF INVENTION
A slide valve for use in throttling solids flow, preferably including a pair of opposed discs in bearing contact with the valve seat. The internal valve construction is unitized which simplifies removal as a single assembly, and permits quick reassembly as well as adjustment. The discs are retained by guide bars to insure a back and forth motion. The valve discs can provide central discharge to reduce flow impingement on the conduit wall which avoids or minimizes erosion, or they can be operated singly and/or independently or in conjunction with each other to provide flow control. The load bearing and guide surfaces are protected from erosion by appropriately located hard-surfacing the integrally reinforced refractory.
A slide valve for use in throttling solids flow, preferably including a pair of opposed discs in bearing contact with the valve seat. The internal valve construction is unitized which simplifies removal as a single assembly, and permits quick reassembly as well as adjustment. The discs are retained by guide bars to insure a back and forth motion. The valve discs can provide central discharge to reduce flow impingement on the conduit wall which avoids or minimizes erosion, or they can be operated singly and/or independently or in conjunction with each other to provide flow control. The load bearing and guide surfaces are protected from erosion by appropriately located hard-surfacing the integrally reinforced refractory.
Description
B~CKGROIIND OF THE IN~7E~ITION
2 Slide valves generally are used for three general
3 types of services including the throttling of flue gas con-
4 taining solid particles, and the throttling and/or blocking of solids flow. This type of valve is used extensively in 6 fluid catalytic cracking units (FCCUs), fluid coking units 7 (FCU's), fluidized iron ore units (FIOR's) and other fluid-8 ized solids units where service conditions may vary between 9 ambient and 1600F. over long periods of time and as high as 1800~F. for a short time and pressures range from O to 11 250 psig. In these processes, the operating pressure is 12 controlled by throttling the flow. Of course slide valves 13 also hsve utility in various other processes. Presently, 4 three basic types of valves are used in the type of environ-ment discussed above, including different configurations 16 for vertical and horizontal conduits to account for the 17 orientation of the valve. A conventional slide valve con-18 figuration with the disc(s) in a tongue and groove guide 19 arrangement is disclosed in U.S. Patent 3,726,306.
~ In the case of fluid solids flow, both blocking 21 and throttling valves are used. Generally, however, block-22 ing of solids flow is accomplished by employing a single 23 disc-type valve which covers an opening provided in a fixed 24 orifice plate. The valve usually offers no restriction to flow when it is fully opened, i.e., the orifice opening is 26 equal to the line diameter. Conventional throttling slide 27 valves operate with a reduced port or opening in order to 28 achieve the desired flow control. The ori~ice generally is 29 considerably less thsn the line diameter depending upon the pressure drop required for proper operation. 8ecause the 31 valves are sub~ect to substantially constant (solids) par-32 ticle flow implngement at elevated temperatures which are - 2 - ~
~ ~0~7~ ~0 1 high enough to significantly reduce the physical strength 2 and hardness of the valve material, erosion of these valves 3 $s likely to occur. Erosion can substantially reduce the 4 operating life of this key piece of equipment, which can present a major problem since the valves are a critical 6 component of process units whose economic success is de-7 pendent on long-term uninterrupted operation. Typical 8 prior art valves which have been employed are disclosed in 9 U.S. Patent Nos. 2,217,834; 2,614,789; 2,636,712; and lo 3,370,610.
11 Of these prior art patents, Lubbock, U.S.
12 2,636,712, which is assigned to the assignee of the present 13 invention, appears most pertinent in that it discloses a 14 slide valve/internals configuration for the flow control of solids. However, the primary emphasis of L~bbock is to 16 co~lpensate for erosion of valve internals by repositioning 17 the discs relative to the seat. One or a plurality of ports 18 (seats) can be provided in the valve orifice plates. The 19 slides are spaced apart a desired distance to provide the desired orifice flow area. As the slides and/or orifice 21 plates erode in the area of flow, the slide discs are moved 22 (with the distance between maintained) relative to the open-23 ings in the orifice plate so that the eroded areas of the 24 valve internals are removed from the flow exposure and dif-ferent nonworn portions of the valve are exposed to the 26 erosive action of the flow. Neither Lubbock or the other 27 prior art valves have the specific construction details of 28 the present invention or provide for a variable flow area 29 or other advantages afforded thereby.
SUMMARY OF THE INVENTION
31 Accordingly, it is a primary object of the pres-32 ent invention to provide a slide valve which will avoid the ' ~07 ~ O ~0 .
l deficience~ of the prior art valves described heretofore.
2 Another primary object of the present invention 3 is to provide a slide valve which will operate in substan-4 tially any positlon.
~ further primary object of the present invention 6 is to provide an improved slide valve having capability to 7 provide a variable flow area.
8 A further object is to provide a slide valve hav-9 ing a unitized internal construction whi~h simplifies re-moval of the internals and permits easy reassembly and ll adjustment.
12 Another object of the invention is to provide a 13 slide valve with improved erosion protection.
14 Still yet a further object of the present inven-tlon is to provide an improved slide valve wherein the 16 sl~des are in bearing contact with the valve seat and the 17 movement of the discs is restrained to a back and forth 18 motion, and is capable of use with substantially any valve 19 operator.
~ According to the present invention, there is pro-21 vided a multi-position double disc slide valve which is es-22 pecially useful in erosive and/or high temperature service.
23 The valve has a fixed orifice and a pair of solid discs 24 which are restrained for back and forth, i.e., reciprocating, movement for creating a variable size flow orifice=which 26 makes the valves suitable for either throttling or blocking 27 service. The discs are not capable of achieving gas tight 28 shutoff because of inadequate seating force developed be-29 tween the discs and the seat by the differential pressure 3~ and/or the sealing surfaces cannot be economically fabricated 3l to the necessary tolerances. They are automatically actu-32 ated by the suitable conventional operators such as air ~07 7 O ~O
1 motor, hydraulic cylinder, pneumatic cylinder and/or di-2 aphragms and the like. Because of their unique construction 3 and arrangement, the valves are particularly effective and 4 useful under extremely erosive conditions such as fluidized solids service. Each of the discs employ a separate oper-6 ator which increases reliability of the valves. This allows 7 one operator can be serviced while the other is in opera-8 tion. When throttling, the valve discs are supported by and 9 are in intimate, direct bearing contact with the orifice plate or seat, whether the valve is mounted in a horizontal 11 or vertical line, with downflow, or in any intermediate 12 position. When the valve is in the closed position but 13 without differential pressure forcing the discs against the 14 seat the guides prevent the discs fromdisengagement for valves installed in horizontal lines. Erosion control of 16 th~ valve internals is accomplished by refractory (integrally 7 reinforced) and hard surfacing on the discs and orifice 18 plate (seat). The valve body is protected with refractory 19 linings. The internals of the valve which are susceptible to erosion are designed with a unitized feature to facili-21 tate their replacement in a simple manner without the need 22 for removal of the complete valve from the line. These 23 parts include the orifice plate, the discs, and the guides 24` which are secured together by bolting into an assembly as 2s a unit. ~n those instances where severe erosion ~ antici-26 pated, i.e., high differential pressure across the variable 27 orifice in a line containing flow with high solids content, 28 a number of conventional throttling valves (e.g., single 29 disc slide valves) in series have been required to insure a reasonable time period between plant shutdowns. Where 31 space limitations do not permit the installation of two 32 or more single disc slide valves in series, a double disc
~ In the case of fluid solids flow, both blocking 21 and throttling valves are used. Generally, however, block-22 ing of solids flow is accomplished by employing a single 23 disc-type valve which covers an opening provided in a fixed 24 orifice plate. The valve usually offers no restriction to flow when it is fully opened, i.e., the orifice opening is 26 equal to the line diameter. Conventional throttling slide 27 valves operate with a reduced port or opening in order to 28 achieve the desired flow control. The ori~ice generally is 29 considerably less thsn the line diameter depending upon the pressure drop required for proper operation. 8ecause the 31 valves are sub~ect to substantially constant (solids) par-32 ticle flow implngement at elevated temperatures which are - 2 - ~
~ ~0~7~ ~0 1 high enough to significantly reduce the physical strength 2 and hardness of the valve material, erosion of these valves 3 $s likely to occur. Erosion can substantially reduce the 4 operating life of this key piece of equipment, which can present a major problem since the valves are a critical 6 component of process units whose economic success is de-7 pendent on long-term uninterrupted operation. Typical 8 prior art valves which have been employed are disclosed in 9 U.S. Patent Nos. 2,217,834; 2,614,789; 2,636,712; and lo 3,370,610.
11 Of these prior art patents, Lubbock, U.S.
12 2,636,712, which is assigned to the assignee of the present 13 invention, appears most pertinent in that it discloses a 14 slide valve/internals configuration for the flow control of solids. However, the primary emphasis of L~bbock is to 16 co~lpensate for erosion of valve internals by repositioning 17 the discs relative to the seat. One or a plurality of ports 18 (seats) can be provided in the valve orifice plates. The 19 slides are spaced apart a desired distance to provide the desired orifice flow area. As the slides and/or orifice 21 plates erode in the area of flow, the slide discs are moved 22 (with the distance between maintained) relative to the open-23 ings in the orifice plate so that the eroded areas of the 24 valve internals are removed from the flow exposure and dif-ferent nonworn portions of the valve are exposed to the 26 erosive action of the flow. Neither Lubbock or the other 27 prior art valves have the specific construction details of 28 the present invention or provide for a variable flow area 29 or other advantages afforded thereby.
SUMMARY OF THE INVENTION
31 Accordingly, it is a primary object of the pres-32 ent invention to provide a slide valve which will avoid the ' ~07 ~ O ~0 .
l deficience~ of the prior art valves described heretofore.
2 Another primary object of the present invention 3 is to provide a slide valve which will operate in substan-4 tially any positlon.
~ further primary object of the present invention 6 is to provide an improved slide valve having capability to 7 provide a variable flow area.
8 A further object is to provide a slide valve hav-9 ing a unitized internal construction whi~h simplifies re-moval of the internals and permits easy reassembly and ll adjustment.
12 Another object of the invention is to provide a 13 slide valve with improved erosion protection.
14 Still yet a further object of the present inven-tlon is to provide an improved slide valve wherein the 16 sl~des are in bearing contact with the valve seat and the 17 movement of the discs is restrained to a back and forth 18 motion, and is capable of use with substantially any valve 19 operator.
~ According to the present invention, there is pro-21 vided a multi-position double disc slide valve which is es-22 pecially useful in erosive and/or high temperature service.
23 The valve has a fixed orifice and a pair of solid discs 24 which are restrained for back and forth, i.e., reciprocating, movement for creating a variable size flow orifice=which 26 makes the valves suitable for either throttling or blocking 27 service. The discs are not capable of achieving gas tight 28 shutoff because of inadequate seating force developed be-29 tween the discs and the seat by the differential pressure 3~ and/or the sealing surfaces cannot be economically fabricated 3l to the necessary tolerances. They are automatically actu-32 ated by the suitable conventional operators such as air ~07 7 O ~O
1 motor, hydraulic cylinder, pneumatic cylinder and/or di-2 aphragms and the like. Because of their unique construction 3 and arrangement, the valves are particularly effective and 4 useful under extremely erosive conditions such as fluidized solids service. Each of the discs employ a separate oper-6 ator which increases reliability of the valves. This allows 7 one operator can be serviced while the other is in opera-8 tion. When throttling, the valve discs are supported by and 9 are in intimate, direct bearing contact with the orifice plate or seat, whether the valve is mounted in a horizontal 11 or vertical line, with downflow, or in any intermediate 12 position. When the valve is in the closed position but 13 without differential pressure forcing the discs against the 14 seat the guides prevent the discs fromdisengagement for valves installed in horizontal lines. Erosion control of 16 th~ valve internals is accomplished by refractory (integrally 7 reinforced) and hard surfacing on the discs and orifice 18 plate (seat). The valve body is protected with refractory 19 linings. The internals of the valve which are susceptible to erosion are designed with a unitized feature to facili-21 tate their replacement in a simple manner without the need 22 for removal of the complete valve from the line. These 23 parts include the orifice plate, the discs, and the guides 24` which are secured together by bolting into an assembly as 2s a unit. ~n those instances where severe erosion ~ antici-26 pated, i.e., high differential pressure across the variable 27 orifice in a line containing flow with high solids content, 28 a number of conventional throttling valves (e.g., single 29 disc slide valves) in series have been required to insure a reasonable time period between plant shutdowns. Where 31 space limitations do not permit the installation of two 32 or more single disc slide valves in series, a double disc
- 5 -.
1 throttling slide valve according to the present invention 2 can be used. The double disc valve then can throttle with 3 one of its slides, while the other slide is maintained in 4 a fully opened position. When the flow control is impaired S because of erosion of the active or operating disc and the
1 throttling slide valve according to the present invention 2 can be used. The double disc valve then can throttle with 3 one of its slides, while the other slide is maintained in 4 a fully opened position. When the flow control is impaired S because of erosion of the active or operating disc and the
6 corresponding section of the fixed orifice (seat), the
7 eroded disc can be moved to its full open position while
8 flow control is assumed with the other uneroded slide and
9 uneroded fixed orifice plate. This capability allows the o subject invention to provide the service life of two con-11 ventional single slide valves in the space of one valve or 12 the service life of four conventional valves in the space 13 required for two valves.
14 ~ Thus, it is apparent that a valve constructed according to the present invention provides a valve design 16 with features which afford low operating costs and relative-17 ly trouble-free maintenance. The valve will operate in es-18 sentially any position in comparison to conventional valvees 19 which now are almost exclusively used in only vertical lines. The internals are easily removed through a detach-21 able bonnet which allows the valve body to be welded into 22 the line to make it leak-free, in place of using a conven-23 tional flange configuration, i.e., bolted line construction 24 for high temperature service which is subjec. to leakage.
The use of such a unitized internal valve construction in 26 downflow and horizontal line valve applications, simplifies 27 the removal and replacement of internals, i.e., one assembly 28 through the use of spares. This configuration permits re-29 pair, reassembly and adjustment in the shop during unit operation, thus avoiding rush type reconditioning without 31 increasing the initial valve cost. The unitized construc-32 tion permits simplified and therefore, more reliable guiding _~,~",j..
of the valve movement. Only one critical dimensional clearance is required in comparison to conventional valves which require at least three such dim,ensional clearances. The operators for the valves have broad flexibility and may comprise any one of a variety of conventional systems (e.g., hydraulic, pneumatic, etc.).
In accordance with a specific embodiment, ~n improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high temperatures comprises, in combin ~ion, (a) a valve body compri~ing a wall defining a central flow passage along a main axis connected by an inlet and outlet for unidirectional flow from said inlet to said outlet and including opposed openings in said wall transverse of said main axis, (b) an orifice plate removably mounted in said valve body between said inlet and outlet and including an orifice opening of fixed dimensions and substantially perpendicular with respect to said main axis, said orifice plate having an i'nlet side which always faces said inlet and an outlet side which always faces said outlet, (c) a pair of opposed disc member~ ~ounted in said valve body in s~bstantially the same plane as said opposed openings for slidiny movement in a direction perpendicular to said main axis of -~aid central flow passage, said disc members located only on said inlet side of said orifice plate and arranged in direct surface bearing contact with said inlet ~ide of said orifice plate for substantially eliminating clearances and fluid bypass between said disc members and said orifice plate, said members con-structed and arranged for providing a variable flow area between opposed inner ed~es with respect to said passage; td) guide means secured with said valve body only on said inlet side of said orifice plate for constraining movement of said discs to a pre-B
~0770~
determined path substantially in the plane o f said opposedopenings in said valve body and preventing substantial transver5e movement of said disc3, and defining together with a portion of said inlet side of said orifice plate the path of movement of said di~cs, and (e) operator mean9 connected for selectively moving each of said discs.
In accordance with a further embodiment, an improved slide valve adap ed for use in the control of processes containing fluid flow with erosive materials and at high temperatures com-prises, in combination: (a) a valve body comprising a walldefining a central flow passageway along a main axis connected by an inlet and an outlet for unidirectional flow from said inlet to said outlet and having opposed openings in said wall transverse of said main axis; (b) an orifice plate removably mounted in said valve body between 5aid inlet and said outlet and having a fixed orifice opening disposed substantially perpendicular with respect to said main axis, said orifice plate having an inlet side which always faces said inlet and an outlet side which always faces said outlet, said orifice plate including refractory means on one surface on said inlet side thereof surrounding said fixed opening and further protective means on said one surface between said refractory means and the outer edges thereof, (c) a pair of opposed di~c members slidably mounted in said valve body sub-stantially in the same plane as said opposed openings only on said inlet side of said orifice plate for sliding movement in direct surface bearing contact with said one surface of said orifice plate in a direction perpendicular to saîd main axis during operation of said valve, said members constructed and arranged for providing variable flow area between opposed inner leading edges thereof with respect to said passageway, refractory means on said discs on the surface thereof facing said inlet and further - 7a ~
lV-~OlV
protective means on opposite surface thereo~ for facilitating relative sliding movement of said discs with respect to said orifice plate, (d) guide means secured with said valve body only on qaid inlet side of said orifice plate on transversely opposite sides of said disc members with respect to their path of movement for constraining movement of said discs in a predetermined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said discs with respect to the path of movement, said guide means having inner surfaces facing said disc members and a coating on said inner surfaces for facilitating relatively free sliding movement between said guide m~ans and said disc members, and defining with a portion of said one surface of said orifice plate the path of movement of said disc members~
In accordance with a still further embodiment, an improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high tempera-ture comprises, in combination: (a) a valve body comprising a wall defining a central flow passageway connected by an inlet and an outlet and having opposed openings in said wall, (b) an orifice plate removably mounted in said valve body between said inlet and said outlet and having a fixed orifice opening disposed sub-stantially perpendicular with respect to the flow through said passageway, ~aid orifice plate including refractory means on one ~urface at least directly adjacent said orifice opening, (c) disc means slidably mounted in ~aid valve body substantially in the same plane as said oppo~ed openings for sliding movement in total bearing surface contact with said one surface of said orifice plate in a direction perpendicular to the axis of said central flow passageway when said valve is operating, said disc means for providing variable flow area with respect to said -7b~-D
~,~r7701~ ' passageway, refractory means on said disc means on the surface thereof facing the direction of flow and further protective means on the opposite surface thereof for facilitating relative sliding movement of said disc means with respect to said orifice plate, (d) guide means secured with said valve body on transversely opposite sides of said disc means with respect to their path of movement for constraining movement of said disc means in a pre-determined path substantially in the plane of said opposed open-ings in said valve body and preventing substantial transverse movement of said disc means with respect to the path of movement, said guide means having inner surfaces facing said disc means and a coating on said inner surfaces for facilitating relatively free sliding movement between said guide means and said disc means.
Having in mind the foregoing that will be evident from an understanding of this disclosure, the invention comprises the construction and arrangement of parts for a valve and its use in fluid solid service as disclosed in the preferred embodiment of the invention, which is hereinafter set forth in such detail as to enable those skilled in the art readily to understand the function, operation, construction and advantages of it when read in conjunction with the accompanying drawings.
BRIEF DESCRIPTIO~ OF THE DRAWINGS
Fig. 1 is a perspective view of a preferred embodiment of a valve constructed and arranged according to the present invention for use in fluids solid service.
Fig. 2 is a top plan view of the valve of Fig. 1.
Fig. 2A shows the operator stem connection with the valve disc.
Fig. 3 is a cross-sectional view taken substantially along the line 3-3 of Fig. 2.
- 7 ~-B
:~077010 Fig. 4 is a cross-sectional view taken ~ubstan-tially along the line 4-4 of Fig. 2.
FigO 5 is a cro~s-sectional view taken substan-tially on the line 5-S of Fig. 1.
Fig. 6 is a top view of the fixed orifice plate used in the valve of the present invention.
Fig. 7 is a cross-sectional view taken substan-tially on the line 7-7 of Fig. 6.
- 7d - .
B' ~0~70~0 1 Pig. 8 is a cross-sectional view taken substan-2 tially on the line 808 of Fig. 6.
3 Fig. 9 is a cross-sectional view of a portion of 4 the disc taken substantially along the line 9-9 of Fig. l.
Fig. lO is a cross-sectional elevation view of 6 reinforced refractory illustrating the anchors according 7 to the present invention taken substantially on the line 8 lO-lO of Fig. 6.
9 Fig. ll is a top view illustrating the reinforced refractory anchor ,arrangement of Fig. lO according to the 11 present invention.
12 Figs~ 12 and 13 are elevational view of the disc 13 guide illustrating the hard surfacing areas thereon.
14 Fig. 14 is a schematic top plan view of a fixed orifice plate having an oblong opening.
16 Fig. 15 is a schematic top plan view of a fixed 17 orifice plate having a circular opening.
18 Fig. 16 is a t~p plan view of an alternate embodi-19 ment of the valve discs having concave leading edges for throttling use.
22 Referring now to the drawings wherein like parts 23 are designated by the same reference numeral throughout the 24 several views, there is disclosed a multi position slide valve lO which is particularly adapted to fluid solid service, 26 especially for throttling flow and more particularly for 27 use in controlling the flow of erosive fluids which contain 28 solids. The valve basically comprises a pair of discs 12, 29 14 which are located diametrically opposite each other ~ across a valve orifice 16 with fixed dimensions. Each slide 31 bears or rests directly on the orifice plate 22. In opera-32 tion one of the discs can be removed from the flow path
14 ~ Thus, it is apparent that a valve constructed according to the present invention provides a valve design 16 with features which afford low operating costs and relative-17 ly trouble-free maintenance. The valve will operate in es-18 sentially any position in comparison to conventional valvees 19 which now are almost exclusively used in only vertical lines. The internals are easily removed through a detach-21 able bonnet which allows the valve body to be welded into 22 the line to make it leak-free, in place of using a conven-23 tional flange configuration, i.e., bolted line construction 24 for high temperature service which is subjec. to leakage.
The use of such a unitized internal valve construction in 26 downflow and horizontal line valve applications, simplifies 27 the removal and replacement of internals, i.e., one assembly 28 through the use of spares. This configuration permits re-29 pair, reassembly and adjustment in the shop during unit operation, thus avoiding rush type reconditioning without 31 increasing the initial valve cost. The unitized construc-32 tion permits simplified and therefore, more reliable guiding _~,~",j..
of the valve movement. Only one critical dimensional clearance is required in comparison to conventional valves which require at least three such dim,ensional clearances. The operators for the valves have broad flexibility and may comprise any one of a variety of conventional systems (e.g., hydraulic, pneumatic, etc.).
In accordance with a specific embodiment, ~n improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high temperatures comprises, in combin ~ion, (a) a valve body compri~ing a wall defining a central flow passage along a main axis connected by an inlet and outlet for unidirectional flow from said inlet to said outlet and including opposed openings in said wall transverse of said main axis, (b) an orifice plate removably mounted in said valve body between said inlet and outlet and including an orifice opening of fixed dimensions and substantially perpendicular with respect to said main axis, said orifice plate having an i'nlet side which always faces said inlet and an outlet side which always faces said outlet, (c) a pair of opposed disc member~ ~ounted in said valve body in s~bstantially the same plane as said opposed openings for slidiny movement in a direction perpendicular to said main axis of -~aid central flow passage, said disc members located only on said inlet side of said orifice plate and arranged in direct surface bearing contact with said inlet ~ide of said orifice plate for substantially eliminating clearances and fluid bypass between said disc members and said orifice plate, said members con-structed and arranged for providing a variable flow area between opposed inner ed~es with respect to said passage; td) guide means secured with said valve body only on said inlet side of said orifice plate for constraining movement of said discs to a pre-B
~0770~
determined path substantially in the plane o f said opposedopenings in said valve body and preventing substantial transver5e movement of said disc3, and defining together with a portion of said inlet side of said orifice plate the path of movement of said di~cs, and (e) operator mean9 connected for selectively moving each of said discs.
In accordance with a further embodiment, an improved slide valve adap ed for use in the control of processes containing fluid flow with erosive materials and at high temperatures com-prises, in combination: (a) a valve body comprising a walldefining a central flow passageway along a main axis connected by an inlet and an outlet for unidirectional flow from said inlet to said outlet and having opposed openings in said wall transverse of said main axis; (b) an orifice plate removably mounted in said valve body between 5aid inlet and said outlet and having a fixed orifice opening disposed substantially perpendicular with respect to said main axis, said orifice plate having an inlet side which always faces said inlet and an outlet side which always faces said outlet, said orifice plate including refractory means on one surface on said inlet side thereof surrounding said fixed opening and further protective means on said one surface between said refractory means and the outer edges thereof, (c) a pair of opposed di~c members slidably mounted in said valve body sub-stantially in the same plane as said opposed openings only on said inlet side of said orifice plate for sliding movement in direct surface bearing contact with said one surface of said orifice plate in a direction perpendicular to saîd main axis during operation of said valve, said members constructed and arranged for providing variable flow area between opposed inner leading edges thereof with respect to said passageway, refractory means on said discs on the surface thereof facing said inlet and further - 7a ~
lV-~OlV
protective means on opposite surface thereo~ for facilitating relative sliding movement of said discs with respect to said orifice plate, (d) guide means secured with said valve body only on qaid inlet side of said orifice plate on transversely opposite sides of said disc members with respect to their path of movement for constraining movement of said discs in a predetermined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said discs with respect to the path of movement, said guide means having inner surfaces facing said disc members and a coating on said inner surfaces for facilitating relatively free sliding movement between said guide m~ans and said disc members, and defining with a portion of said one surface of said orifice plate the path of movement of said disc members~
In accordance with a still further embodiment, an improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high tempera-ture comprises, in combination: (a) a valve body comprising a wall defining a central flow passageway connected by an inlet and an outlet and having opposed openings in said wall, (b) an orifice plate removably mounted in said valve body between said inlet and said outlet and having a fixed orifice opening disposed sub-stantially perpendicular with respect to the flow through said passageway, ~aid orifice plate including refractory means on one ~urface at least directly adjacent said orifice opening, (c) disc means slidably mounted in ~aid valve body substantially in the same plane as said oppo~ed openings for sliding movement in total bearing surface contact with said one surface of said orifice plate in a direction perpendicular to the axis of said central flow passageway when said valve is operating, said disc means for providing variable flow area with respect to said -7b~-D
~,~r7701~ ' passageway, refractory means on said disc means on the surface thereof facing the direction of flow and further protective means on the opposite surface thereof for facilitating relative sliding movement of said disc means with respect to said orifice plate, (d) guide means secured with said valve body on transversely opposite sides of said disc means with respect to their path of movement for constraining movement of said disc means in a pre-determined path substantially in the plane of said opposed open-ings in said valve body and preventing substantial transverse movement of said disc means with respect to the path of movement, said guide means having inner surfaces facing said disc means and a coating on said inner surfaces for facilitating relatively free sliding movement between said guide means and said disc means.
Having in mind the foregoing that will be evident from an understanding of this disclosure, the invention comprises the construction and arrangement of parts for a valve and its use in fluid solid service as disclosed in the preferred embodiment of the invention, which is hereinafter set forth in such detail as to enable those skilled in the art readily to understand the function, operation, construction and advantages of it when read in conjunction with the accompanying drawings.
BRIEF DESCRIPTIO~ OF THE DRAWINGS
Fig. 1 is a perspective view of a preferred embodiment of a valve constructed and arranged according to the present invention for use in fluids solid service.
Fig. 2 is a top plan view of the valve of Fig. 1.
Fig. 2A shows the operator stem connection with the valve disc.
Fig. 3 is a cross-sectional view taken substantially along the line 3-3 of Fig. 2.
- 7 ~-B
:~077010 Fig. 4 is a cross-sectional view taken ~ubstan-tially along the line 4-4 of Fig. 2.
FigO 5 is a cro~s-sectional view taken substan-tially on the line 5-S of Fig. 1.
Fig. 6 is a top view of the fixed orifice plate used in the valve of the present invention.
Fig. 7 is a cross-sectional view taken substan-tially on the line 7-7 of Fig. 6.
- 7d - .
B' ~0~70~0 1 Pig. 8 is a cross-sectional view taken substan-2 tially on the line 808 of Fig. 6.
3 Fig. 9 is a cross-sectional view of a portion of 4 the disc taken substantially along the line 9-9 of Fig. l.
Fig. lO is a cross-sectional elevation view of 6 reinforced refractory illustrating the anchors according 7 to the present invention taken substantially on the line 8 lO-lO of Fig. 6.
9 Fig. ll is a top view illustrating the reinforced refractory anchor ,arrangement of Fig. lO according to the 11 present invention.
12 Figs~ 12 and 13 are elevational view of the disc 13 guide illustrating the hard surfacing areas thereon.
14 Fig. 14 is a schematic top plan view of a fixed orifice plate having an oblong opening.
16 Fig. 15 is a schematic top plan view of a fixed 17 orifice plate having a circular opening.
18 Fig. 16 is a t~p plan view of an alternate embodi-19 ment of the valve discs having concave leading edges for throttling use.
22 Referring now to the drawings wherein like parts 23 are designated by the same reference numeral throughout the 24 several views, there is disclosed a multi position slide valve lO which is particularly adapted to fluid solid service, 26 especially for throttling flow and more particularly for 27 use in controlling the flow of erosive fluids which contain 28 solids. The valve basically comprises a pair of discs 12, 29 14 which are located diametrically opposite each other ~ across a valve orifice 16 with fixed dimensions. Each slide 31 bears or rests directly on the orifice plate 22. In opera-32 tion one of the discs can be removed from the flow path
10'77 0~
1 (shown downward by the arrow, although flow can be in 2 other directions depending on line orientation) while the 3 other is used for flow control and when the used slide is 4 eroded too much for effective control, it can be positioned away from the flow path and the other disc used in lieu 6 thereof. Alternatively, both of the discs can be employed 7 to control flow through the orifice. As shown in Fig. 1, 8 the valve generally designated 10 comprises the pair of 9 opposed solid disc members 12 and 14 having a generally lo rectangular cross-section, with each of the discs squared
1 (shown downward by the arrow, although flow can be in 2 other directions depending on line orientation) while the 3 other is used for flow control and when the used slide is 4 eroded too much for effective control, it can be positioned away from the flow path and the other disc used in lieu 6 thereof. Alternatively, both of the discs can be employed 7 to control flow through the orifice. As shown in Fig. 1, 8 the valve generally designated 10 comprises the pair of 9 opposed solid disc members 12 and 14 having a generally lo rectangular cross-section, with each of the discs squared
11 or straight along its inner or leading edge. This applies
12 primarily to solids flow throttling type valves which
13 block solids flow when the discs are in closed position.
14 When the leading opposed edges of the discs are spaced apart a predetermined distance, they effectively provide 16 the desired orifice opening between the discs. A rectan-17 gular shaped orifice opening 16 (see Fig. 6) is formed 18 centrally in the orifice plate 22 which is disposed on the 19 underside of the discs and is in direct or cintiguous slid-ing contact or relation with the disc members 12 and 14.
21 On the upper side of the disc members 12 and 14 and disposed 22 ad;acent to the transverse sides or edges thereof are a 23 pair of essentially parallel elongated guide bars 24 and 24 26 wh~ch insure that the movement of the slides will be limited to a back and forth motion, thus effectively pre-26 venting undesired up and down movement. Side retainer 27 bars 28 and 30 (see Figs. 5 and 8) are secured with the 28 upper guide bars and are located directly below them along 29 the transverse edges of the discs for containing ~he disc and preventing substantial undesired side to side movement.
31 The transverse spacing is in the range of between about 1/8"
32 to about 3/16". By this type of disc containment o~ly one r ~770~o.
1 truly critical clearance is required by comparison to the 2 three critical clearances normally required in conventional 3 slide valve designs. Thus, the only critical clearance 4 for slide valves according to the present invention is th~t between the undersurface of the upper guides 24, 26 and the 6 upper surface of the disc members 12, 14, which preferably 7 should have a tolerance range of + 0.005 inches. In the 8 typical tongue-in-groove type arrangement, e.g., see U.S.
9 3,726,306, tolerances must be maintained not only for this particular dimensipn but also between the disc(s) and the 11 fixed orifice plate (ver~ical) and between the discs and 12 the tonguie-and-groove guides in the horizontal direction 13 on each side of the discs. The typical movement of the 14 discs can best be seen by reference to Fig. 2, wherein the discs 12, 14 shown in solid lines correspond to the posi-16 tions shown in Fig. l. When the discs are moved inwardly 17 toward each other so that their leading edge surfaces 18 18 and 20 contact each other the valve is in the closed posi-19 tio~-As further shown in Fig. 2, the line A is repre-21 sentative of the maximum opening between the discs, where-22 as line B represents the opening normally employed during 23 operation of the valve. The dotted centerline C represents 24 the center of the fixed orifice opening 16 and corresponds to total valve closure, i.e., there is no minimum opening 26 for the type of disc design where the leading disc edges 27 are in abutting contact (e.g. squared or straight edge).
28 If the length of the discs is equal to or slightly greater than the maximum orifice diameter or opening, then only one ~ of the discs can be used to close the valve provided that 31 the other disc has been placed in 8 fully retracted position.
32 Other variations in the size of the disc are, of course, 10770~
1 possible and will occur to those sk;.lled in the art in 2 order to accommodate a desired flow pattern. An alternate 3 embodiment for the discs is shown in Fig. 16 wherein the 4 leading edge of each disc includes a concave portion 17 S which is centrally located of the disc sides. This con-6 struction is useful when there is no need for shut-off 7 since these always will be a minimum opening (shown 8 by the dotted line) with the discs in their innermost 9 or closed position. Thus, it will have utility when lo throttling is desired (e.g. flue gas pressure control).
11 The upper and transverse disc guide bars are secured to-12 gether by means of a plurality of threaded bolts 32 such 13 as shown in Fig. 4. The annular orifice plate 22 is mounted 14 to a lower annular support member 34 by means of bolting as shown by 36 and extends radially inward therefrom about 16 the fixed orifice 16 (e.g. rectangular). Although in the 17 preferred embodiment the orifice opening is shown as sub-18 stantially rectangular, it is within the scope of this in-19 vention and contemplated to have other shapes. For example, the opening may be oblong (see Fig. 14) or circular (see 21 Fig. 15). The fixed opening by having its major axis a~
22 l~gned in the direction of the valve stems will insure a 23 more centralized flow from the variable orifice between the 24 discs to minimize erosive impingement of solids on the i 25 valve body. Of course, the fixed orifice opening is sized 26 to provide desired rangeability and control of the flow.
27 The outer end of the annular support 34 is welded about its 2~ periphery shown at 38 to the inner wall of the generally 29 circular cylindrical valve body 40 which contains the ori-fice plate, discs and guides. The support 34 is additionally 31 supported on its underside by a plurality of circumfer-32 entially spaced radial-extended gussets 42. The valve body 107'70~V
l is connected at one side (the inlet in the preferred em-2 bodiment) to the carbon steel line 44 which forms part of 3 the process flow line in which the valve is used and at its 4 bottom or outlet side is connected to another carbon steel line 46.
6 The valve discs generally operate or move in a 7 plane perpendicular with respect to the process flow 8 through the line. In the valve body there are a psir of 9 diagonally opposite openings 48, 50 which accommodate the back and forth or recipr~cating movement of the respective ll discs. Through these openings extend stems 52 which 12 are connected at one end by "Tee" bar ends, 51 and 53 in 13 recesses 56 and 58 (see Fig. 2A) respectively in the discs 14 12 and 14 and at their other end or outer extremities to operators 60 and ~2 in a conventional ma~ner. As previously l6 explained, the operator may be of the penumatic, hydraulic ~7 or other conventional type, e.g., air motor, electric motor, 18 hydraulic or air piston/cylinder system or diap~ragm. T~e l9 operators 60 and 62 are identical and both are connected 20~ to the discs in the same manner. The stems 52 pass through 21 pedestals 64. Coaxial with the stems are anti-rotation nuts 22 66 which prevents any tendency of the stems to turn or ro-23 tate as the disc reciprocates, which in turn prevents any 24 rotational tendencies of the disc members. The nuts 66 are contained within a groove 68 provided in the pedestals.
26 ~uring valve operation diagonally opposite openings 48, 27 50 in the valve body, are covered by rectangular bonnet 28 covers 70 having a central opening 72 in which is mounted 29 a standard stuffing box 74 (i.e., compressible packing rings arranged around stems 52 which pass through opening 31 72 and concentrically through 74). The stuffing box is 32 secured to the mounting cover by welding. Brackets 76 r .
1~77010 1 reinforce the pedestal base flanges 77 and 78. The bonnet 2 cover 70 is removably mounted by means of bolts disposed 3 about its perimeter and secured to the extended bonnet 4 flange 80 and gussets. The bonne~ cover and mou~ting sup-ports the operators radially outward from the valve body.
6 Appropriate connections are made to power the operator hy-7 draulically, by air, electrically, etc., as the case may be.
8 Thus, it is seen that a double disc arrangement 9 according to the present invention can center the discharge 0 flow in the process line, which substantially reduces flow 11 impingement on the inner pipe walls. Or the discs can be 12 used for throttling by maintaining one disc for throttling 13 purposes with the other maintained in a full open position, 14 i.e.~ fully withdrawn, and when erosion limits the flow control attainable the eroded disc is moved to its full 16 open position and the other or second disc then is used to 17 control the flow. This is essentially like having two valves 18 in one and makes the valve especially suitable for applica-1~ tions where long operating periods (runs) are desired, but space limitations preclude installation of a second or third 21 valve. Also, by ensuring that the discs are always in con-22 tact with the seat regardless of the valve orientation, 23 erosion resulting from bypass flow between ~he discs and 24 seat is avoided (in conventional valve a clearance is pro- -;
vided which permits such flow). While the disc and seat 26 may not always be in intimate contact, e.g., when the valve 27 is mounted in a vertical line with upward flow, the valve 28 still will operate satisfactory in such orientation so long 29 as the pressure drop across the valve is greater than the opposite weight effect of the discs, which is a matter of 31 deslgn within the scope of the invention. This pressure 32 differential will cause the discs to maintain bearing con-~7010 1 tact with the orifice plate. When the slides arè in bear-2 ing contact, any flow which might normally bypass between 3 the disc and the seat is thus eliminated. Also, because of 4 this large surface to surface contact, the thrust force due to the differential pressure drop across the valve is car 6 ried by the seat and not by the valve discs or guides.
7 This then permits a reduction in the thickness of the discs 8 which are fully supported by the seat. In conventional 9 valves the discs are supported by the tongue and groove guides at the extreme width of the discs thereby subjecting 11 the discs to the full pressure thrust in a bending mode of 12 loading. Maintenance of the valve according to the present 13 invention is particularly simplified because of its unitized 14 internal construction and is facilitated by the full access bonnet opening through which the internals assembly can be 16 removed as a single unit after unbolting the bolts 36 and 17 removing the bonnet cover. To reduce the cost one large 18 bonnet can be used rather than two. For the latter case the 19 stuffing box 74 is provided directly in the valve body as well as the support arrangement 77 and 78 for the operator 2~ pedestal 64.
22 The desired erosion protection is accomplished by 23 providin~ hardsurfacing and integrally reinforced refrac-24 tory as discussed in detail hereinafter. The hardsurfacing may comprise a material such as Stellite 6 or some other 26 suitable anti-galling material, i.e., on which would prevent 27 the well-known phenomenon of welding of the sliding mater-28 ials together. Stellite 6 is a high temperature hard 29 surfacing material which is applied by a welding process and is characterized by being an extremely hard and wear resist-31 ant coating. The hardsurfacing which is deslgnated by 82 32 throughout is employed on all of the load bearing surfaces ~ '70 i~
1 of the fixed orifice, on the guide surfaces facing the 2 discs and on the load bearing surfaces of the discs which 3 face the orifice plate, and is best shown in Figs. 6 through 4 9. On the orifice plate 22 the hardsurfacing 32 is disposed about the plate periphery and extends outward of the ori-6 fice periphery, adjacent to either end and adjacent the 7 guides on either side of the plate.
8 Reinforced refractory generally designated 84 is 9 also disposed about and directly adjacent the orifice open-lo ing 16 on all sides thereof inward of the hardsurfacing.
11 While various types of refractory can be used9 a suitable 1~ one may basically comprise a high alumina chemical setting 13 refractory with at least 89% tubular alumina. The re-14 fractory is compounded wlth phosphoric acid to develop suitable bonding. A number of commercially available re-16 fractories used for this type of service are made by Re-17 fractories Specialties Co. (Resco) A22 and Babcock and 18 Wilcox Kosphos 30. The refractory is integrally reinforced 19 with well-distributed alloy fibers which are approximately 3/4" to 1" long and of 0.010"-0.013" diameter or with a 21 rectangular cross section approximately 0.010" x 0.030". ;
22 The fibers are added to the refractory while it is being 23 mixed at a typical ratio of between 1/2 volume % to 2 volume r 24 %. The former represents a weight of 2.4 pounds of fiber per cubic foot of refractory, while the latter is 9.6 26 pounds per cubic foot of refractory. The reinforced re- ;
27 fractory 84 is disposed on the load bearing top side of the 28 orifice plate 22 at 86 surrounding the orifice opening 16, wrapping around the vertical walls at 88 defining the open-ing 16, and extending along the bottom side of the plate 31 at 90 directly adjacent the opening. See Flgs. 6 and 7.
32 In a typical construction, the refractory 84 extends from
21 On the upper side of the disc members 12 and 14 and disposed 22 ad;acent to the transverse sides or edges thereof are a 23 pair of essentially parallel elongated guide bars 24 and 24 26 wh~ch insure that the movement of the slides will be limited to a back and forth motion, thus effectively pre-26 venting undesired up and down movement. Side retainer 27 bars 28 and 30 (see Figs. 5 and 8) are secured with the 28 upper guide bars and are located directly below them along 29 the transverse edges of the discs for containing ~he disc and preventing substantial undesired side to side movement.
31 The transverse spacing is in the range of between about 1/8"
32 to about 3/16". By this type of disc containment o~ly one r ~770~o.
1 truly critical clearance is required by comparison to the 2 three critical clearances normally required in conventional 3 slide valve designs. Thus, the only critical clearance 4 for slide valves according to the present invention is th~t between the undersurface of the upper guides 24, 26 and the 6 upper surface of the disc members 12, 14, which preferably 7 should have a tolerance range of + 0.005 inches. In the 8 typical tongue-in-groove type arrangement, e.g., see U.S.
9 3,726,306, tolerances must be maintained not only for this particular dimensipn but also between the disc(s) and the 11 fixed orifice plate (ver~ical) and between the discs and 12 the tonguie-and-groove guides in the horizontal direction 13 on each side of the discs. The typical movement of the 14 discs can best be seen by reference to Fig. 2, wherein the discs 12, 14 shown in solid lines correspond to the posi-16 tions shown in Fig. l. When the discs are moved inwardly 17 toward each other so that their leading edge surfaces 18 18 and 20 contact each other the valve is in the closed posi-19 tio~-As further shown in Fig. 2, the line A is repre-21 sentative of the maximum opening between the discs, where-22 as line B represents the opening normally employed during 23 operation of the valve. The dotted centerline C represents 24 the center of the fixed orifice opening 16 and corresponds to total valve closure, i.e., there is no minimum opening 26 for the type of disc design where the leading disc edges 27 are in abutting contact (e.g. squared or straight edge).
28 If the length of the discs is equal to or slightly greater than the maximum orifice diameter or opening, then only one ~ of the discs can be used to close the valve provided that 31 the other disc has been placed in 8 fully retracted position.
32 Other variations in the size of the disc are, of course, 10770~
1 possible and will occur to those sk;.lled in the art in 2 order to accommodate a desired flow pattern. An alternate 3 embodiment for the discs is shown in Fig. 16 wherein the 4 leading edge of each disc includes a concave portion 17 S which is centrally located of the disc sides. This con-6 struction is useful when there is no need for shut-off 7 since these always will be a minimum opening (shown 8 by the dotted line) with the discs in their innermost 9 or closed position. Thus, it will have utility when lo throttling is desired (e.g. flue gas pressure control).
11 The upper and transverse disc guide bars are secured to-12 gether by means of a plurality of threaded bolts 32 such 13 as shown in Fig. 4. The annular orifice plate 22 is mounted 14 to a lower annular support member 34 by means of bolting as shown by 36 and extends radially inward therefrom about 16 the fixed orifice 16 (e.g. rectangular). Although in the 17 preferred embodiment the orifice opening is shown as sub-18 stantially rectangular, it is within the scope of this in-19 vention and contemplated to have other shapes. For example, the opening may be oblong (see Fig. 14) or circular (see 21 Fig. 15). The fixed opening by having its major axis a~
22 l~gned in the direction of the valve stems will insure a 23 more centralized flow from the variable orifice between the 24 discs to minimize erosive impingement of solids on the i 25 valve body. Of course, the fixed orifice opening is sized 26 to provide desired rangeability and control of the flow.
27 The outer end of the annular support 34 is welded about its 2~ periphery shown at 38 to the inner wall of the generally 29 circular cylindrical valve body 40 which contains the ori-fice plate, discs and guides. The support 34 is additionally 31 supported on its underside by a plurality of circumfer-32 entially spaced radial-extended gussets 42. The valve body 107'70~V
l is connected at one side (the inlet in the preferred em-2 bodiment) to the carbon steel line 44 which forms part of 3 the process flow line in which the valve is used and at its 4 bottom or outlet side is connected to another carbon steel line 46.
6 The valve discs generally operate or move in a 7 plane perpendicular with respect to the process flow 8 through the line. In the valve body there are a psir of 9 diagonally opposite openings 48, 50 which accommodate the back and forth or recipr~cating movement of the respective ll discs. Through these openings extend stems 52 which 12 are connected at one end by "Tee" bar ends, 51 and 53 in 13 recesses 56 and 58 (see Fig. 2A) respectively in the discs 14 12 and 14 and at their other end or outer extremities to operators 60 and ~2 in a conventional ma~ner. As previously l6 explained, the operator may be of the penumatic, hydraulic ~7 or other conventional type, e.g., air motor, electric motor, 18 hydraulic or air piston/cylinder system or diap~ragm. T~e l9 operators 60 and 62 are identical and both are connected 20~ to the discs in the same manner. The stems 52 pass through 21 pedestals 64. Coaxial with the stems are anti-rotation nuts 22 66 which prevents any tendency of the stems to turn or ro-23 tate as the disc reciprocates, which in turn prevents any 24 rotational tendencies of the disc members. The nuts 66 are contained within a groove 68 provided in the pedestals.
26 ~uring valve operation diagonally opposite openings 48, 27 50 in the valve body, are covered by rectangular bonnet 28 covers 70 having a central opening 72 in which is mounted 29 a standard stuffing box 74 (i.e., compressible packing rings arranged around stems 52 which pass through opening 31 72 and concentrically through 74). The stuffing box is 32 secured to the mounting cover by welding. Brackets 76 r .
1~77010 1 reinforce the pedestal base flanges 77 and 78. The bonnet 2 cover 70 is removably mounted by means of bolts disposed 3 about its perimeter and secured to the extended bonnet 4 flange 80 and gussets. The bonne~ cover and mou~ting sup-ports the operators radially outward from the valve body.
6 Appropriate connections are made to power the operator hy-7 draulically, by air, electrically, etc., as the case may be.
8 Thus, it is seen that a double disc arrangement 9 according to the present invention can center the discharge 0 flow in the process line, which substantially reduces flow 11 impingement on the inner pipe walls. Or the discs can be 12 used for throttling by maintaining one disc for throttling 13 purposes with the other maintained in a full open position, 14 i.e.~ fully withdrawn, and when erosion limits the flow control attainable the eroded disc is moved to its full 16 open position and the other or second disc then is used to 17 control the flow. This is essentially like having two valves 18 in one and makes the valve especially suitable for applica-1~ tions where long operating periods (runs) are desired, but space limitations preclude installation of a second or third 21 valve. Also, by ensuring that the discs are always in con-22 tact with the seat regardless of the valve orientation, 23 erosion resulting from bypass flow between ~he discs and 24 seat is avoided (in conventional valve a clearance is pro- -;
vided which permits such flow). While the disc and seat 26 may not always be in intimate contact, e.g., when the valve 27 is mounted in a vertical line with upward flow, the valve 28 still will operate satisfactory in such orientation so long 29 as the pressure drop across the valve is greater than the opposite weight effect of the discs, which is a matter of 31 deslgn within the scope of the invention. This pressure 32 differential will cause the discs to maintain bearing con-~7010 1 tact with the orifice plate. When the slides arè in bear-2 ing contact, any flow which might normally bypass between 3 the disc and the seat is thus eliminated. Also, because of 4 this large surface to surface contact, the thrust force due to the differential pressure drop across the valve is car 6 ried by the seat and not by the valve discs or guides.
7 This then permits a reduction in the thickness of the discs 8 which are fully supported by the seat. In conventional 9 valves the discs are supported by the tongue and groove guides at the extreme width of the discs thereby subjecting 11 the discs to the full pressure thrust in a bending mode of 12 loading. Maintenance of the valve according to the present 13 invention is particularly simplified because of its unitized 14 internal construction and is facilitated by the full access bonnet opening through which the internals assembly can be 16 removed as a single unit after unbolting the bolts 36 and 17 removing the bonnet cover. To reduce the cost one large 18 bonnet can be used rather than two. For the latter case the 19 stuffing box 74 is provided directly in the valve body as well as the support arrangement 77 and 78 for the operator 2~ pedestal 64.
22 The desired erosion protection is accomplished by 23 providin~ hardsurfacing and integrally reinforced refrac-24 tory as discussed in detail hereinafter. The hardsurfacing may comprise a material such as Stellite 6 or some other 26 suitable anti-galling material, i.e., on which would prevent 27 the well-known phenomenon of welding of the sliding mater-28 ials together. Stellite 6 is a high temperature hard 29 surfacing material which is applied by a welding process and is characterized by being an extremely hard and wear resist-31 ant coating. The hardsurfacing which is deslgnated by 82 32 throughout is employed on all of the load bearing surfaces ~ '70 i~
1 of the fixed orifice, on the guide surfaces facing the 2 discs and on the load bearing surfaces of the discs which 3 face the orifice plate, and is best shown in Figs. 6 through 4 9. On the orifice plate 22 the hardsurfacing 32 is disposed about the plate periphery and extends outward of the ori-6 fice periphery, adjacent to either end and adjacent the 7 guides on either side of the plate.
8 Reinforced refractory generally designated 84 is 9 also disposed about and directly adjacent the orifice open-lo ing 16 on all sides thereof inward of the hardsurfacing.
11 While various types of refractory can be used9 a suitable 1~ one may basically comprise a high alumina chemical setting 13 refractory with at least 89% tubular alumina. The re-14 fractory is compounded wlth phosphoric acid to develop suitable bonding. A number of commercially available re-16 fractories used for this type of service are made by Re-17 fractories Specialties Co. (Resco) A22 and Babcock and 18 Wilcox Kosphos 30. The refractory is integrally reinforced 19 with well-distributed alloy fibers which are approximately 3/4" to 1" long and of 0.010"-0.013" diameter or with a 21 rectangular cross section approximately 0.010" x 0.030". ;
22 The fibers are added to the refractory while it is being 23 mixed at a typical ratio of between 1/2 volume % to 2 volume r 24 %. The former represents a weight of 2.4 pounds of fiber per cubic foot of refractory, while the latter is 9.6 26 pounds per cubic foot of refractory. The reinforced re- ;
27 fractory 84 is disposed on the load bearing top side of the 28 orifice plate 22 at 86 surrounding the orifice opening 16, wrapping around the vertical walls at 88 defining the open-ing 16, and extending along the bottom side of the plate 31 at 90 directly adjacent the opening. See Flgs. 6 and 7.
32 In a typical construction, the refractory 84 extends from
15 -~ ~,~
1~7'701~
1 the opening 16 outward about 8" on the top side and approx-2 imately 4" on the bottom side. On the discs 12, 14 (see 3 Fig. 9), the refractory 84 is disposed completely on the 4 top side at 92 and on the side surface at 94, as well as 5 for about 4" inwardly from the ends on the bottom side as 6 shown at 96. The construction of the discs is identical 7 and therefore, only one is illustrated and discussed in 8 detail. Also on the bottom surface disc inward of the re-g fractory is the hardsurfacing 82, since that portion is in contact with the o~ifice plate 22. Typically, the refrac-11 tory lining has a thickness of 2" and is supported and 12 fastened in place by a plurality of wire anchor loops 98 13 which are wleded as shown at 100 to the surfaces 102 of the 14 valve which are to be reEractory lined. These loops may, for ex~mple, comprise 1/8" diameter wire welded at their
1~7'701~
1 the opening 16 outward about 8" on the top side and approx-2 imately 4" on the bottom side. On the discs 12, 14 (see 3 Fig. 9), the refractory 84 is disposed completely on the 4 top side at 92 and on the side surface at 94, as well as 5 for about 4" inwardly from the ends on the bottom side as 6 shown at 96. The construction of the discs is identical 7 and therefore, only one is illustrated and discussed in 8 detail. Also on the bottom surface disc inward of the re-g fractory is the hardsurfacing 82, since that portion is in contact with the o~ifice plate 22. Typically, the refrac-11 tory lining has a thickness of 2" and is supported and 12 fastened in place by a plurality of wire anchor loops 98 13 which are wleded as shown at 100 to the surfaces 102 of the 14 valve which are to be reEractory lined. These loops may, for ex~mple, comprise 1/8" diameter wire welded at their
16 contact point with the vaive surface and ext.ending longitu-
17 dinally in transverse spaced relation. The loops would ex
18 tend with their raised portions or lands shown at 104
19 located about midway of the thickness of the reinforced lin-ing, being welded in place to the valve surface at their 21 contact points. The wire loops can be transversely spaced 22 apart approximately 3" and are staggered longitudinally so 23 that for adjacent loops the welds of one are generally op-24 posite the raised portion of the other, as best shown in 25 Fig. 11.
26 While a particular preferred embodiment of the in-27 vention has been shown and described and certain modifica-28 tions thereof suggested, it will be understood that the t~ue 29 spirit and scope of the invention as set forth in the ap-pended claims which embrace other modifications and embodi-31 ments which will occur to those of ordinary skill in the 32 art.
26 While a particular preferred embodiment of the in-27 vention has been shown and described and certain modifica-28 tions thereof suggested, it will be understood that the t~ue 29 spirit and scope of the invention as set forth in the ap-pended claims which embrace other modifications and embodi-31 ments which will occur to those of ordinary skill in the 32 art.
Claims (28)
1. An improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high temperatures comprising in combination:
(a) a valve body comprising a wall defining a central flow passage along a main axis connected by an inlet-and outlet for unidirectional flow from said inlet to said outlet and including opposed openings in said wall transverse of said main axis;
(b) an orifice plate removably mounted in said valve body between said inlet and outlet and including an orifice opening of fixed dimensions and sub-substantially perpendicular with respect to said main axis, said orifice plate having an inlet side which always faces said inlet and an outlet side which always faces said outlet:
(c) a pair of opposed disc members mounted in said valve body in substantially the same plane as said opposed openings for sliding movement in a direction perpendicular to said main axis of said central flow passage, said disc members located only on said inlet side of said orifice plate and arranged in direct surface bearing contact with said inlet side of said orifice plate for substantially eliminating clearances and fluid bypass between said disc members and said orifice plate, said members constructed and arranged for providing a variable flow area between opposed inner edges with respect to said passage;
(d) guide means secured with said valve body only on said inlet side of said orifice plate for constraining movement of said discs to a pre-determined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said discs, and defining together with a portion of said inlet side of said orifice plate the path of movement of said discs; and (e) operator means connected for selectively moving each of said discs.
(a) a valve body comprising a wall defining a central flow passage along a main axis connected by an inlet-and outlet for unidirectional flow from said inlet to said outlet and including opposed openings in said wall transverse of said main axis;
(b) an orifice plate removably mounted in said valve body between said inlet and outlet and including an orifice opening of fixed dimensions and sub-substantially perpendicular with respect to said main axis, said orifice plate having an inlet side which always faces said inlet and an outlet side which always faces said outlet:
(c) a pair of opposed disc members mounted in said valve body in substantially the same plane as said opposed openings for sliding movement in a direction perpendicular to said main axis of said central flow passage, said disc members located only on said inlet side of said orifice plate and arranged in direct surface bearing contact with said inlet side of said orifice plate for substantially eliminating clearances and fluid bypass between said disc members and said orifice plate, said members constructed and arranged for providing a variable flow area between opposed inner edges with respect to said passage;
(d) guide means secured with said valve body only on said inlet side of said orifice plate for constraining movement of said discs to a pre-determined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said discs, and defining together with a portion of said inlet side of said orifice plate the path of movement of said discs; and (e) operator means connected for selectively moving each of said discs.
2. The valve of claim 1 including removable cover means externally disposed of said valve body over said openings for facilitating removal of said disc members, said orifice plate and said guide means from within said valve body.
3. The valve of claim 1 wherein each of said disc members comprises a substantially rectangular configuration with squared ends at said innermost edges.
4. The valve of claim 2 wherein each of said disc members include on their inner edges a flat portion extending from opposite transverse sides thereof inwardly toward said main axis for a predetermined distance and a concave portion being disposed between said flat portions on each of said disc members.
5. The valve of claim 1 wherein said guide means com-prises a transverse member having a flat inner surface and a guide member extending inwardly toward said main axis and secured with said transverse member on opposite sides of the path of movement of said disc members for constraining movement of said members to a substantially reciprocating motion, said flat inner surface extending toward said inlet for the full height of said disc member and said guide member overlying at least a portion of the surface of said disc members facing said inlet.
6. The valve of claim 1 wherein said disc members are constructed such that they are maintained in substantially con-tinuous surface bearing contact between opposed transverse extremities thereof with the adjacent surface of said orifice plate.
7. The valve of claim 1 wherein said guide means, disc members and orifice plate comprise a substantially unitary assembly thereby facilitating removal from said valve body through said openings.
8. The valve of claim 1 wherein said guide means comprises first and second members with guide surfaces of pre-determined height located on each transversely opposite side of said disc members with respect to the path of movement of said discs, said disc members having transverse sides which are coextensive with the height of said guide surfaces along the flow passage axis, said first member disposed substantially close to and uniformly spaced from the adjacent transverse side of said members and said second member disposed substantially adjacent and overlying at least a portion of the surface of said members, whereby movement of said slide members is constrained such that said members are maintained in surface bearing contact with said orifice plate during operation of said valve.
9. The valve of claim 8 wherein each of said transverse sides of said members are transversely spaced with respect to said first member in the range of between about 1/8 inch to about 3/16 inch and the tolerance between the surface of said disc member facing said inlet and said second member is about + 0.005.
10. The valve of claim 1 including a protective layer on the load-bearing and sliding surfaces of said orifice plate, said disc members and said guide means.
11. The valve of claim 1 wherein each of said disc members has a squared surface along its inner leading edge such that when said discs are disposed in their fully closed position said leading edges are in continuous abutting relationship.
12. The valve of claim 1 wherein the fixed opening in said orifice plate is substantially circular.
13. The valve of claim 1 wherein the fixed opening in said orifice plate is substantially rectangular.
14. The valve of claim 1 wherein the fixed opening in said orifice plate is elongated.
15. The valve of claim 1 wherein said guide means includes inner surfaces facing said disc members, said surfaces having a protective layer for maintaining relative free sliding relationship between said disc members and said guide means.
16. The valve of claim 1 wherein the leading inner edges of said disc members includes central concave opposed portions such that said disc members define a minimum opening when disposed in their innermost closed position.
17. The valve of claim 1 wherein each of said disc members includes refractory means on the top and sides thereof and further protective means on the bottom thereof.
18. The valve of claim 1 wherein said orifice plate includes refractory means surrounding the fixed opening and further protective means disposed on said plate in the area between said refractory means and the outer edges thereof.
19. The valve of claim 1 wherein said disc members each comprises a continuous solid member within its extremeties.
20. An improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high temperatures comprising in combination:
(a) a valve body comprising a wall defining a central flow passageway along a main axis connected by an inlet and an outlet for uni-directional flow from said inlet to said outlet and having opposed openings in said wall transverse of said main axis:
(b) an orifice plate removably mounted in said valve body between said inlet and said outlet and having a fixed orifice opening disposed substantially perpendicular with respect to said main axis, said orifice plate having an inlet side which always faces said inlet and an outlet side which always faces said outlet, said orifice plate including refractory means on one surface on said inlet side thereof surrounding said fixed surfaces for facilitating relatively free sliding movement between said guide means and said disc members, and defining with a portion of said one surface of said orifice plate the path of movement of said disc members.
(a) a valve body comprising a wall defining a central flow passageway along a main axis connected by an inlet and an outlet for uni-directional flow from said inlet to said outlet and having opposed openings in said wall transverse of said main axis:
(b) an orifice plate removably mounted in said valve body between said inlet and said outlet and having a fixed orifice opening disposed substantially perpendicular with respect to said main axis, said orifice plate having an inlet side which always faces said inlet and an outlet side which always faces said outlet, said orifice plate including refractory means on one surface on said inlet side thereof surrounding said fixed surfaces for facilitating relatively free sliding movement between said guide means and said disc members, and defining with a portion of said one surface of said orifice plate the path of movement of said disc members.
21. The valve of claim 20 wherein said refractory means wraps around the sides of said disc members in facing relation-ship with respect to said guide means.
22. The valve of claim 20 wherein the side of said disc member facing said orifice plate comprises said one surface for enabling relative free sliding with respect to said orifice plate.
23. The valve of claim 20 wherein said disc members are continuously solid and within its extremeties.
24. An improved slide valve adapted for use in the control of processes containing fluid flow with erosive materials and at high temperature comprising in combination:
(a) a valve body comprising a wall defining a central flow passageway connected by an inlet and an outlet and having opposed openings in said wall;
(b) an orifice plate removably mounted in said valve body between said inlet and said outlet and having a fixed orifice opening disposed substantially perpendicular with respect to the flow through said passageway, said orifice plate including refractory means on one surface at least directly adjacent said orifice opening;
(c) disc means slidably mounted in said valve body substantially in the same plane as said opposed openings for sliding movement in total bearing surface contact with said one surface of said orifice plate in a direction perpendicular to the axis of said central flow passageway when said valve is operating, said disc means for providing variable flow area with respect to said passageway, refractory means on said disc means on the surface thereof facing the direction of flow and further protective means on the opposite surface thereof for facilitating relative sliding movement of said disc means with respect to said orifice plate;
(d) guide means secured with said valve body on transversely opposite sides of said disc means with respect to their path of movement for constraining movement of said disc means in a predetermined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said disc means with respect to the path of movement, said guide means having inner surfaces facing said disc means and a coating on said inner surfaces for facilitating relatively free sliding movement between said guide means and said disc means.
(a) a valve body comprising a wall defining a central flow passageway connected by an inlet and an outlet and having opposed openings in said wall;
(b) an orifice plate removably mounted in said valve body between said inlet and said outlet and having a fixed orifice opening disposed substantially perpendicular with respect to the flow through said passageway, said orifice plate including refractory means on one surface at least directly adjacent said orifice opening;
(c) disc means slidably mounted in said valve body substantially in the same plane as said opposed openings for sliding movement in total bearing surface contact with said one surface of said orifice plate in a direction perpendicular to the axis of said central flow passageway when said valve is operating, said disc means for providing variable flow area with respect to said passageway, refractory means on said disc means on the surface thereof facing the direction of flow and further protective means on the opposite surface thereof for facilitating relative sliding movement of said disc means with respect to said orifice plate;
(d) guide means secured with said valve body on transversely opposite sides of said disc means with respect to their path of movement for constraining movement of said disc means in a predetermined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said disc means with respect to the path of movement, said guide means having inner surfaces facing said disc means and a coating on said inner surfaces for facilitating relatively free sliding movement between said guide means and said disc means.
25. The valve of claim 24 wherein said disc means comprises a pair of opposed disc members whose leading inner edges are adjustable relative to each other for providing opening and further protective means on said one surface between said refractory means and the outer edges thereof;
(c) a pair of opposed disc members slidably mounted in said valve body substantially in the same plane as said opposed openings only on said inlet side of said orifice plate for sliding movement in direct surface bearing contact with said one surface of said orifice plate in a direction perpendicular to said main axis during operation of said valve, said members constructed and arranged for providing variable flow area between opposed inner leading edges thereof with respect to said passageway, refractory means on said discs on the surface thereof facing said inlet and further protective means on opposite surface thereof for facilitating relative sliding movement of said discs with respect to said orifice plate;
(d) guide means secured with said valve body only on said inlet side of said orifice plate on transversely opposite sides of said disc members with respect to their path of movement for constraining movement of said discs in a pre-determined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said discs with respect to the path of movement, said guide means having inner surfaces facing said disc members and a coating on said inner variable flow therebetween.
(c) a pair of opposed disc members slidably mounted in said valve body substantially in the same plane as said opposed openings only on said inlet side of said orifice plate for sliding movement in direct surface bearing contact with said one surface of said orifice plate in a direction perpendicular to said main axis during operation of said valve, said members constructed and arranged for providing variable flow area between opposed inner leading edges thereof with respect to said passageway, refractory means on said discs on the surface thereof facing said inlet and further protective means on opposite surface thereof for facilitating relative sliding movement of said discs with respect to said orifice plate;
(d) guide means secured with said valve body only on said inlet side of said orifice plate on transversely opposite sides of said disc members with respect to their path of movement for constraining movement of said discs in a pre-determined path substantially in the plane of said opposed openings in said valve body and preventing substantial transverse movement of said discs with respect to the path of movement, said guide means having inner surfaces facing said disc members and a coating on said inner variable flow therebetween.
26. The valve of claim 1 wherein said disc members include opposed transverse flat sides which extend in the direction of said main axis between opposed surfaces of said members.
27. The valve of claim 26 wherein said flat sides , are uniformly spaced from an inner flat guide surface of said guide means.
28. The valve of claim 1 wherein said disc members include a bearing contact surface which extends between transverse extremities of each of said disc members and said bearing contact surface is substantially in total surface contact with the adjacent surface of said orifice plate.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US74741176A | 1976-12-21 | 1976-12-21 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1077010A true CA1077010A (en) | 1980-05-06 |
Family
ID=25004948
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA288,687A Expired CA1077010A (en) | 1976-12-21 | 1977-10-11 | Multi-position disc slide valve |
Country Status (9)
| Country | Link |
|---|---|
| JP (1) | JPS6030870B2 (en) |
| BE (1) | BE862035A (en) |
| CA (1) | CA1077010A (en) |
| DE (1) | DE2744268A1 (en) |
| FR (1) | FR2375521A1 (en) |
| GB (1) | GB1587875A (en) |
| IT (1) | IT1087986B (en) |
| NL (1) | NL7712793A (en) |
| SE (1) | SE432983B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253774A (en) * | 2020-09-30 | 2021-01-22 | 内蒙古工业大学 | High-speed motion mechanism of mechanical pressure relief cabin door |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4182359A (en) * | 1977-12-27 | 1980-01-08 | Combustion Engineering, Inc. | Slide gate damper |
| CA1186672A (en) * | 1981-11-23 | 1985-05-07 | Frank J. Jandrasi | Control valve for flow of solids |
| FR2542839B1 (en) * | 1983-03-14 | 1985-08-16 | Voroshilovgrad Mashinostr | PIPE REGISTER |
| DE3403766C2 (en) * | 1984-02-03 | 1986-12-11 | J.M. Voith Gmbh, 7920 Heidenheim | Slide valve |
| DE3516356A1 (en) * | 1985-05-07 | 1986-11-13 | Verwaltungs Lohse GmbH & Co KG, 7920 Heidenheim | SHUT-OFF VALVE FOR CONTROLLING THE FLOW OF HIGH-FLUID MEDIA PROVIDED WITH HIGH DIRTY PARTS |
| US5205998A (en) * | 1985-08-01 | 1993-04-27 | Ethyl Corporation | Angle of repose valve |
| DE102011052963B4 (en) | 2011-08-24 | 2016-05-19 | Ikn Gmbh | Klinkerofenanlage with slide for Tertiärluftleitung |
| CN103836218B (en) * | 2012-11-22 | 2016-05-11 | 中国石油天然气集团公司 | A kind of coking tower valve |
| CN104603509B (en) * | 2013-08-30 | 2017-03-08 | 戴科知识产权控股有限责任公司 | The elastic gate valve that can be moved by solenoid actuator |
| JP6516700B2 (en) * | 2016-04-06 | 2019-05-22 | 東都電機工業株式会社 | Shutter opening and closing device |
| CN107906216B (en) * | 2017-11-28 | 2023-12-19 | 徐州新南湖科技有限公司 | Colliery gas adsorbs control valve |
| CN109681647B (en) * | 2018-12-21 | 2021-04-20 | 浙江意格特机械制造有限公司 | Energy-saving type air inlet valve of variable frequency compressor for mine |
| CN112049951A (en) * | 2020-09-14 | 2020-12-08 | 苏州颂康智能科技有限公司 | Dangerous chemical substance leakage prevention system in bridge drainage ditch body |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2636712A (en) * | 1950-04-03 | 1953-04-28 | Standard Oil Dev Co | Slide valve for regulating the flow of solids |
| DE1087419B (en) * | 1956-01-27 | 1960-08-18 | Waldenmaier J E H | Regulating slide for lines carrying thick matter |
| DE1287380B (en) * | 1966-11-22 | 1969-01-16 | Werkzeugmaschinenfabrik Vogtla | Method for producing a pair of guides, in particular for flat and prismatic guides on machine tools |
| GB1204069A (en) * | 1968-05-16 | 1970-09-03 | C B P Engineering & Constructi | Improvements in or relating to the supply of pulverised fuel to boilers |
| US3964507A (en) * | 1975-01-13 | 1976-06-22 | Tapco International, Inc. | Slide valve with integrated removable internals |
| US3976094A (en) * | 1975-01-13 | 1976-08-24 | Tapco International, Inc. | Guided slide valve |
-
1977
- 1977-09-27 GB GB4016677A patent/GB1587875A/en not_active Expired
- 1977-10-01 DE DE19772744268 patent/DE2744268A1/en active Granted
- 1977-10-11 CA CA288,687A patent/CA1077010A/en not_active Expired
- 1977-11-11 IT IT2960977A patent/IT1087986B/en active
- 1977-11-21 NL NL7712793A patent/NL7712793A/en active Search and Examination
- 1977-11-22 FR FR7735098A patent/FR2375521A1/en active Granted
- 1977-11-28 JP JP14171877A patent/JPS6030870B2/en not_active Expired
- 1977-12-20 SE SE7714534A patent/SE432983B/en not_active IP Right Cessation
- 1977-12-20 BE BE2056531A patent/BE862035A/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112253774A (en) * | 2020-09-30 | 2021-01-22 | 内蒙古工业大学 | High-speed motion mechanism of mechanical pressure relief cabin door |
Also Published As
| Publication number | Publication date |
|---|---|
| SE7714534L (en) | 1978-06-22 |
| DE2744268A1 (en) | 1978-06-22 |
| GB1587875A (en) | 1981-04-08 |
| FR2375521B1 (en) | 1984-01-27 |
| BE862035A (en) | 1978-06-20 |
| SE432983B (en) | 1984-04-30 |
| JPS5378423A (en) | 1978-07-11 |
| JPS6030870B2 (en) | 1985-07-18 |
| IT1087986B (en) | 1985-06-04 |
| DE2744268C2 (en) | 1987-10-29 |
| FR2375521A1 (en) | 1978-07-21 |
| NL7712793A (en) | 1978-06-23 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4253487A (en) | Multi-position dual disc slide valve | |
| CA1077010A (en) | Multi-position disc slide valve | |
| US4664139A (en) | Valve especially for controlling particulate solids flow | |
| US4693452A (en) | Valve | |
| US5368276A (en) | Valve with truncated aperture providing enhanced rangeability and logarithmic flow characteristic | |
| US4174728A (en) | Sliding-gate valve | |
| US4275763A (en) | Double-slide valve | |
| US3937247A (en) | Valve for fluids containing abrasive particles | |
| US6488263B2 (en) | Valve stem and method of manufacture; improved stem packing | |
| US5799928A (en) | Ball valve with improved valve seat and bonnet assembly | |
| US5895028A (en) | Single disc slide valve with center biased flow | |
| US4542763A (en) | Butterfly valve assembly and method of making same | |
| US4389037A (en) | Double disc gate vale with replaceable spacer ring | |
| US4410002A (en) | Valve provided with a thermally-actuated mechanism for pressing valve seats against a valve gate body | |
| US20230106275A1 (en) | Catalyst control and withdrawal valve with tight shutoff capability | |
| AU640678B2 (en) | Throttling valve | |
| US4498498A (en) | Double valve assembly | |
| CA1280336C (en) | Control valve | |
| US4331316A (en) | Shut-off valve for high temperature erosive flow | |
| RU2109194C1 (en) | Adjusting gate valve | |
| US6247679B1 (en) | Valve stem and method of manufacture; improved stem packing | |
| CN214662159U (en) | High-temperature-resistant wear-resistant lining gate valve | |
| EP0279569B1 (en) | Sliding plate valve | |
| US2336694A (en) | Valve | |
| RU2105914C1 (en) | Valve |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |