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US3561479A - Noninterflow rotary valve and improved fluid seals - Google Patents

Noninterflow rotary valve and improved fluid seals Download PDF

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Publication number
US3561479A
US3561479A US3561479DA US3561479A US 3561479 A US3561479 A US 3561479A US 3561479D A US3561479D A US 3561479DA US 3561479 A US3561479 A US 3561479A
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Prior art keywords
ports
rotor
rotors
housing
central portion
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Lyle J Archer
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    • 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
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • F16K11/074—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces
    • F16K11/0743—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces with both the supply and the discharge passages being on one side of the closure plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86638—Rotary valve

Definitions

  • a housing has upper and lower pressure chambers separated by a housing central portion, each chamber containing a pivotal rotor adjacent the central portion.
  • the housing central portion has first and second ports, each opening into both chambers against the rotors, a third port opening only into the upper chamber and a fourth port opening only into the lower chamber.
  • Each rotor has two ports therethrough so that in alternate positions, the upper rotor ports communicate with the central portion third port and alternately with the central portion first and second ports, while the lower rotor ports communicate with the central portion fourth port and alternately with the central portion second and first ports.
  • the rotors are connected simultaneously pivotal and spool seals are mounted in the ends of the central portion ports against the rotors permitting such rotor pivoting.
  • OBJECTS AND SUMMARY or THE INVENTION 1 It is, therefore, an object of this invention to provide a rotary valve adapted for simultaneously transmitting two fluid flow streams there'through and switching said streams between various thereof ,wherein stream interflow within said valve and pressure loss of said streams is greatly minimized, if not virtually completelyeliminated.
  • the basic concept of the valve includes the provision of a single stationary housing portion between two separate pressure chambers, each chamber having a separate controlling rotor therein.
  • the housing and rotor ports directing the separate fluid streams through the valve are arranged so that only one fluid stream flows through each of the pressure chambers in a given position of the valve, alternate positioning of the valve either redirecting each of said fluid streams through the same pressure chambers or, more preferably, switching the direction of individual stream flow to the other pressure chamber.
  • valve stationary housing may be provided with a single pressure or inlet port through which there is always fluid inflow, a single exhaust or outlet port from which there is always fluid outflow, and two working ports which are alternately fluid inflow and outflow ports, said latter two working ports being those connected to a working mechanism controlled by the rotary valve.
  • the inlet and outlet ports of the rotary valve are connected to each of the pressure chambers and the two working ports are connected to one each of the pressure chambers.
  • the individual rotors may. have the ports thereof arranged so that movement of.
  • the two rotors for the pressure chambers are preferably simultaneously movable and the relative locations of the housing and rotor ports are such that all housing ports are effectively blocked for an interval between flow communicating positions of the rotors, resulting in maximum noninterflow characteristics despite the simultaneous fluid flow control of two fluid streams through the rotary valve.
  • a rotary valve which may include parts or all of the foregoing advantageous characteristics and construction, and may further include unique forms of spool-type seals engaged between the valve stationary housing and the valve rotors producing extremely effective fluid seals for optimum noninterflow characteristics while still permitting ease of pivotal movement and positioning of the valve rotors.
  • the spool-type seals are preferably mounted in annular recesses surrounding the stationary housing ports urged axially into abutment with radial surfaces of the rotors and having resilient sealing rings arranged therein for maximum scaling in particular directions of fluid flow dependent on the more important fluid flow direction to or from that particular port.
  • the unique spooltype seals included in the preferred form of rotary valve of the pr :sent invention may also have advantageous use and application in various other types of valves and fluid flow devices wherein fluid flow streams are directed between ports of adjacent members, and particularly where it is necessary to provide relative movement between said members while maintaining said port sealing
  • Other objects and advantages of the invention will be apparent from the following specification and the accompanying drawings which are for the purpose of illustration only.
  • FIG. 1 is a perspective view of a preferred embodiment of a rotary valve incorporating the principles of the present invention
  • FIG. 2 is an enlarged, vertical sectional view looking in the direction of the arrows 2-2 in FIG. 1;
  • FIG. 3 is an enlarged, fragmentary, vertical sectional view taken from FIG. 2 and showing one form of spool-type seal of the present invention
  • FIG. 4 is a view similar to FIG. 3 but showing another form of spool-type seal of the present invention
  • FIG. 5 is a reduced, horizontal sectional view looking in the direction of the arrows 5-5 in FIG. 2;
  • FIG. 6 is a reduced, horizontal sectional view looking in the direction of the arrows 6-6 in FIG. 2;
  • FIG. 7 is a reduced, horizontal sectional view looking in the direction of the arrows 7-7 in FIG. 2;
  • FIG. 8 is a reduced, horizontal sectional view looking in the direction of the arrows 8-8 in FIG. 2;
  • FIG. 9 is a fragmentary, vertical sectional view looking in the direction of the arrows 9-9 in FIG. 2 and showing certain of the valve housing fluid flow ports in hidden lines and certain other of said housing ports in phantom lines to illustrate the relative positioning thereof.
  • a preferred embodiment of rotary valve including the principles of the present invention is shown in the drawings and includes a generally cylindrical, stationary housing generally indicated at It) formed by a central housing portion l2 axially spacing or separating upper and lower housing portions 14 and 16, all of said housing portions preferably being formed of stainless steel or the like with the upper and lower housing portions being secured to the central housing portion by a series of appropriate fasteners 18.
  • Generally cylindrical pressure chambers 20 and 22 are formed in the upper and lower housing portions 14 and 16, the upper pressure chamber being substantially identical to the lower pressure chamber except axially reverse and each being enclosed by its respective upper or lower housing portion with the exception of opening axially against the central housing portion 12.
  • a centrally located positioning shaft 24 is received axially through the central housing portion 12 extending downwardly into the lower pressure chamber 22 and upwardly through both of the upper pressure chamber 20 and the upper housing portion 14.
  • a generally cylindrical upper rotor 26 is positioned in the upper pressure chamber 20 substantially radially spanning said upper pressure chamber with a lower surface 28 thereof axially adjacent the central housing portion 12, and a similar lower rotor 30 is similarly positioned in the lower pressure chamber 22 with an upper surface 32 adjacent the central housing portion.
  • the upper and lower rotors 26 and 30 receive the positioning shaft 24 axially therethrough and are appropriately keyed to the positioning shaft for rotatable or pivotal movement therewith.
  • thrust bearings 34 are mounted in the central housing portion 12 axially abutting the upper rotor lower surface 28 and the lower rotor upper surface 32, the upper rotor 26 being retained downwardly against the upper of the thrust bearings 34 by a shaft collar 36 and the lower rotor 30 being retained upwardly against the lower of the thrust bearings 34 by a nut 38 on the lower end of the positioning shaft 24.
  • Resilient sealing O-rings 44 are positioned surrounding the positioning shaft 24 at the upper and lower extremities of the central housing portion 12 sealing radially between said shaft and central housing portion preventing fluid flow axially along the positioningshaft between the upper and lower pressure chambers 20 and 22 while still permitting rotation of the positioning shaft relative to the central housing portion.
  • Similar sealing Q-ring 46 is positioned around the positioning shaft 24 upwardly of the upper pressure chamber 20 and the shaft collar 36 sealing radially between the positioning shaft and the upper housing portion 14 preventing fluid flow axially along the positioning shaft and upwardly through the upper housing portion 14.
  • similar sealing O-ririgs 48 are positioned around the central housing portion I2 above and below the thrust bearings 34 between the central housing portion and the upper and lower housing portions 14 and I6 preventing fluid flow from the upper and lower pressure chambers 20 and 22 between these housing portions.
  • first and second housing ports 50 and 52 are formed through the central housing portion 12, each communicating with both of the upper and lower pressure chambers 20 and 22 as will be hereinafter explained more in detail.
  • third and fourth housing ports 54 and 56 are formed through the central housing portion 12, the third housing port communicating with only the upper pressure chamber 20 and the fourth housing port communicating with only the lower pressure chamber 22. All of the first through fourth housing ports 50, 52, 54 and 56 open into the respective upper and lower pressure chambers 20 and 22 axially toward and against the upper and lower rotors 26 and 30 so that the rotors are positioned for controlling fluid flow through these housing ports, depending on the particular positioning of the rotors.
  • the first housing port 50 includes a primary part 58 extending radially into the central housing portion 12 and connected secondary upper and lower parts 60 and 62 extending axially through said central housing portion and respectively to the upper and lower pressure chambers 20 and 22, the second housing port 52 including the similarly extending primary part 64, secondary upper part 66 and secondary lower part 68 Furthermore, as best determined by a comparison of FIGS.
  • the secondary upper and lower parts 60 and 62 of the first housing port 50 are circumferentially offset or at opposite circumferential sides of and communicating with the primary part 58 of said first housing port, while the secondary upper and lower parts 66 and 68 of the second housing port 52 are similarly circumferentially offset at opposite citcumferential sides of the primary part 64 of said second housing port.
  • the secondary upper parts 60 and 66 of the first and second housing ports 50 and 52 are shown in phantom lines and the secondary lower parts 62 and 68 thereof are shown in broken lines to indicate such relative circumferential offset positioning.
  • center lines of the secondary upper parts 60 and 66 of the first and second housing ports 50 and 52 are circumferentially spaced l communicating with common sides of the primary parts 58 and 64 of said housing ports asviewed in FIG. 6, and the center lines of the secondary. lower parts 62 and 68 of the first and second housing ports 50 and 52 are spaced apart 120 in the opposite circumferential direction and communicate with the opposite sides of the primary parts 58 and 64 of said housing ports as viewed in FIG. 7.
  • the third housing port 54 extends radially and then axially to the upper pressure chamber20 on right angle coincident center lines as best seen in FIGS. 2 and 6, the fourthhousing port 56 extending similarly to the lower pressure chamber 22 as best seen in FIGS. 2 and 7.
  • the third housing port 54 opens into the upper pressure chamber 20 with the center line thereof spaced 120 between the center lines of the first and second housing ports 50 and-52 as shown in FIG. 6, while the fourth housing port 56 opens into the lower pressure chamber. 22 with the center line thereof ofiset 120 between the center lines of the first and second housing ports 50 and 52 as shownin FIG. 7.
  • first, second and third housing ports 50, 52 and 54 open axially into the upper pressure chamber ZO'againstthe upper rotor 26 substantially equally circumferentially spaced about the central housing portion 12, and the first, second and fourth housing ports 50, 52 and 56 open axially into the lower pressure chamber 22 against the lower rotor equally circumferentially spaced about the central housing portion 12 but circumferentially between said port openings into the upper pressure chamber.
  • the upper rotor 26 has two ports 70 formed axially therethrough withthe center lines of said ports being spaced apart.
  • the lower rotor 30 has two ports 72 formed axially therethrough with the center lines of said ports spaced 120 apart.
  • the upperrotor ports 70 may therefore be positioned alternately in communication with the first and third housing ports 50 and 54 or the second and third housing ports 52'and 54, and the lower rotor ports 72 may be positioned in communication alternately with the first and fourth housing ports 50 and 56 or the second and fourth housing ports 52 and 56.
  • the various ports of the central housing portion 12 and the upper and lower rotors 26 and 30 are therefore positioned in relation to each other so that the upper pressure chamber 20 can only communicate one at a time with the first and second housing ports 50 and 52 and the lower pressure chamber 22 can only communicate one at a time with said first and second housing ports. Furthermore, when the upper pressure chamber 20 is in communication with the first housing port 50, the lower pressure chamber 22 is in communication with the second housing portion 52, and when the upper pressure chamber is in communication with the second housing port, the lower pressure chamber is in communication with the first housing port, the two pressure chambers never being in communication with the same of the first and second housing ports in the particular arrangement shown.
  • the positioning shaft 24 projects upwardly through the upper housing portion 14 with the upper end thereof telescoped by a positioning cap 74 pivotally overlying the upper housing portion.
  • the positioning cap 74 is secured to the positioning shaft 24 by a connecting pin 76, whereby, pivotal movement of the positioning cap causes consequent pivotal movement of the positioning shaft for pivoting the upper and lower rotors 26 and 30 between their alternate positions in the manner hereinbefore described.
  • Such alternate positions of the upper and lower rotors 26 and 30 is preferably determined by a positioning pin 78 mounted in the upper housing portion 14 and projecting upwardly into an arcuate positioning slot80 formed in and opening downwardly of the positioning cap 74, the extremities of the positioning slot determining the upper and lower rotor alternate positions.
  • a spring urged positioning ball 82 mounted in the upper housing portion 14 for upward reception in a series of spaced, arcuate, positioning recesses 84 in and opening downwardly of the positioning cap 74, the positioning recesses being appropriately spaced for determining the various positions of the upper and lower rotors.
  • spool-type seals are arranged in the various first, second, third and fourth housing ports 50, 52, 54 and 56 at the ends of these ports against the upper and lower rotors 26 and 30.
  • the spool-type seal of FIG. 3 is preferably mounted in each of the first, third and fourth housing ports 50, 54 and 56, said seal being arranged for providing maximum sealing qualities when fluid is flowing 1 from that particular housing port toward the upper'or lower rotor 26 or 30 and toward the upper or lower pressure chamber 20 or 22, although a certain amount of sealing is provided by this seal for fluid flow in the reversedirection.
  • each of the two second housing ports 52 is mounted in each of the two second housing ports 52 and is particularly adapted for sealing fluid where fluid flow is from the upper or lower pressure chamber 20 or 22 through the upper or'lower rotor 26' or 30 into the central housing portion 12 since the fluid flow in these second housing ports 52 will always be in this direction in a particular embodiment of rotary valve shown.
  • a spool-type seal generally indicated at 86 is received in an annular recess generally indicated at 88 of the central housing portion 12 surrounding the end of one branch of the first housing port 50, said recess 88 opening axially endwise toward, in this particular case, the lower radial surface 29 of the upper rotor 26 and forming a radial annular end surface 90 axially spaced from the recess open end and a cylindrical annular wall 92 extending axially from said end surface 90 to the recess open end.
  • the recess 88 also preferably includes an auxiliary recess portion 94 radially outwardly offset form the main part of recess 88 at the open end of the first port 50 in the central housing portion 12.
  • the auxiliary recess portion 94 is likewise annular opening radially into the first housing port 50 forming a part of the recess cylindrical wall 97. and opening endwise toward the upper rotor 26.
  • the seal 86 includes rigid, annular sealing spool 96 axially movable, preferably slidable, along the recess cylindrical wall 92 with an annular, reduced radial section 98 axially aligned with and axially movable in the auxiliary recess portion 94. Furthermore, the reduced radial section 98 of the sealing spool 96 axially abuts the lower radial surface 28 of the upper rotor 26 while forming a relieved end surface I00 around the sealing spool 96. The sealing spool 96 terminates axially away from the upper rotor 26 within the recess 88 axially spaced from the recess end surface 90.
  • the seal 86 further includes an annular, preferably radially flat, guard ring 102 in the recess 88 axially adjacent the sealing spool 96, a resilient sealing ring 104 in the recess axially adjacent the guard ring, a rigid, annular backing spool 106 in the recess axially adjacent the sealing ring 104, and an annular spring 108 in the recess axially between the backing spool and the recess end surface 90.
  • the backing spool 106 is axially movable, preferably slidable, along the recess cylindrical wall 92 and has a radially reduced section 110 extending radially inwardly of and axially along the sealing ring 1114 and the guard ring 102, movably telescoped by the sealing spool 96.
  • the reduced section 110 of the backing spool 106 therefore, confines the guard ring 102 and sealing ring 104 between this reduced section and the recess Cylindrical wall 92 as shown.
  • the guard ring 102 closely slidably abuts the recess cylindrical wall 92 to prevent the sealing ring 104 from extruding axially along this guard ring and between the sealing spool es and the recess cylindrical wall upon the sealing ring being axially deformed or flattened by fluid flow pressure axially against said sealing ring from between the backing spool 1G6 and the recess cylindrical wall.
  • the spring 108 is preferably a deformed, washer-type spring reacting axially between the backing spool 1116 and the recess end surface 90 while occupying a minimum axial space of the recess 88.
  • the spring 108 may be formed of spring steel, and the sealing and backing spools 96 and 11% may be formed of stainless steel, metal being preferred partic ularly where high fluid pressures are involved.
  • the guard ring 102 may be of plastic, such as one of the usual memory plastics, and the sealing ring 104 may be a usual resilient material O-ring.
  • a seal generally indicated at 112 is mounted in a recess generally indicated at 116 at the ends of the second housing ports 52 in the central housing portion 12, the particular second housing port shown being that opening axially against the upper rotor 26.
  • the fluid flow of the second housing ports 52 of the particular embodiment of rotary valve illustrated is always from the upper and lower pressure chambers 20 and 22 axially into said second housing ports so that the seal 112 is particularly adapted for such flow.
  • the recess 114 is somewhat similar to that for the seal 86 and, in this case, is annular surrounding the ends of the second housing ports 52 opening axially toward the lower radial surface 28 of the upper rotor 26 forming an annular end surface 116 spaced axially from the upper rotor 26 and an annular, cylindrical wall 116 extending axially from said end surface to said open end.
  • the seal 112 includes a rigid, annular sealing spool 1211 having a main section 122 primarily within the recess 114i and movable, preferably slidable, axially along the recess cylindrical wall 118.
  • the sealing spool main section 122 is axially spaced from the recess end surface 116 and has a reduced radial section 12d extending axially from said main section 122 axially past the recess end surface within the second housing port 52, although closely radially adjacent said end surface inner extremity as shown.
  • the sealing spool 120 further has a reduced radial section 126 preferably axially aligned with the reduced radial section 124, but projecting axially from the main section 122 toward and abutting the lower surface 28 of the upper rotor 26 and forming a relieved end surface 128 on said sealing spoolmain section 122.
  • the seal 112 further includes an axially reacting spring 130 axially between the sealing spool main section 122 and the recess end surface 116, a rigid backup ring 132 axially adjacent said spring, a resilient sealing ring 134 axially adjacent said backup ring, and a guard ring 136 axially between said sealing ring and the recess end surface 116.
  • All of the spring 130, backup ring 132, sealing ring 134 and guard ring 136 are radially confined by the sealing spool reduced radial section 124 between said reduced radial section and the recess cylindrical wall 118, the backup ring 132 being axially movable, preferably slidable, between said sealing spool reduced radial section 124 and the recess cylindrical wall 18 and the guard ring 136 at least closely slidably abutting the sealing spool reduced radial section 124.
  • the sealing spool and backup ring may again be formed of stainless steel, the washer-type spring 1300f spring steel and the guard ring 136 of memory plastic, with the sealing ring 134 a usual O-ring.
  • the guard ring 136 prevents axial extrusion of the sealing ring 134 along the reduced radial section 124 of the sealing spool 120, and the spring acts axially against both the sealing spool main section 122 and the backup ring 132.
  • the spring pressure axially against the sealing spool main section 122 forces the reduced radial section 126 into abutment with the upper rotor 26, while the relieved end surface 128 of the sealing spool 120 somewhat balances this axial sealing pressure permitting ease of movement of the rotors.
  • first housing port 50 is connected to a source of fluid under pressure for receiving fluid into the rotary valve
  • second housing port 52 is connected back to said fluid source for directing exhaust fluid to said source
  • third and fourth housing ports 54 and 56 are connected to opposite ends of a double acting, fluid actuated cylinder.
  • fluid will exhaust from the opposite end of the fluid cylinder into and through the fourth housing port 56 downwardly through one of the lower rotor ports 72 into the lower pressure chamber 22, upwardly through the other of the lower rotor ports 72 into the second housing port 52, and through and from said second housing port ounvardly exhausting back to the source of fluid.
  • Pivoting the positioning shaft 24 to pivot the upper and lower rotors 26 and 30 simultaneously to their alternate positions will axially align the upper rotor ports 70 with the second and third housing ports 52 and $4, and the lower rotor ports 72 with the first and fourth housing ports 50 and 56, thereby reversing the fluid flow through the upper and lower pressure chambers 20 and 22, and reversing the fluid flow through the third and fourth housing ports 54 and 56.
  • a rotary valve having a unique construction including two pressure chambers 20 and 22 incorporated in a minimumsize valve housing which permits the formation of a true, noninterflow rotary valve.
  • the provision of the separate pressure chambers and 22 permits proper spacing of the various housing and rotor ports required for such interflow characteristics without the necessity of either increasing the overall rotary valve size or reducing the capacity thereof for a given valve size.
  • a rotary valve including axially spaced upper and lower portions separated by a central portion; a pressure chamber formed in each of 'said housing upper and lower ortions opening axially against said housing central portion; a rotor pivotal between at least two positions in each of said upper and lower pressure chambers axially adjacent said housing central portiom spaced first, second, third and fourth ports through said housing central portion and into certain of said pressure chambers, said first and second ports opening into each of said pressure chambers against said rotors thereof, said third port opening into said upper pressure chamber against said upper chamber rotor and being free of opening into said lower pressure chamber, said fourth port openinginto said lower pressure chamber against said lower chamber rotor andbeing free of opening into said upper pressure chamber; two particularly positioned ports through each of said rotors communicating axially between said housing central portion and the respective of said pressure chambers,
  • said ports of said upper chamber rotor communicating through said upper chamber rotor and said upper pressure chamber between at least said first and third housing central portion ports when said upper chamber rotor is in one of said positions and between at least said second and third housing central portion ports when said upper chamber rotor is in the other of saidpositions, said ports of said lower chamber rotor communicating through said lower chamber rotor and said lower pressure chamber between at least said second and fourth housing central portion ports when said lower chamber rotor is in one of said positions and between at least said first and fourth housing central portion ports when said lower chamber rotor is in the other of said positions; and positioning means for pivoting said rotors between their two positions.
  • a rotary valve as defined in claim 1 in which said rotors and said housing central portion are constructed and said ports thereof respectively arranged so that each of said rotors seals off one of said ports of said housing central portion in each of said rotor positions.
  • a rotary valve as defined in claim 1 in which said positioning means is operably connected to both of said rotors for simultaneously pivoting said rotors between each rotor two positions, said positioning'means operable connection placing both of said rotors simultaneously in their one position and simultaneously in their other position.
  • each of said rotors is constructedand the ports thereof arranged sealing off at least one of said housing central portion ports previously communicating with at least one of said rotor ports prior to said at least one rotor ports communicating with another of said housing central portion ports during said pivotal movements of said rotors by said positioning; means.
  • a rotary valve as defined in claim 1 in which said rotors are constructed and said ports thereof arranged sealing off all of said housing central portion ports during an interval of rotorpivotal movement by said positioning means between said rotor two positions.
  • annular sealing means is positioned in certain of said housing central portion ports resiliently urged abutting radial surfaces of said rotor for forming a fluid seal axially between said housing central portion and said rotors while permitting pivotal movements of said rotors relative to said housing central portion by said rotor positioning means.
  • each of said rotors is constructed and said ports thereof arranged for pivotal movement of said rotors through substantially l20 between said rotor two positions.
  • a rotary valve as defined in claim 1 in which said rotor positioning means is operably connected to said rotors for simultaneously pivoting said rotors between said rotor two positions, said rotors each being in said one position simultaneously and in, said other position simultaneously; and in which said two ports of each rotor are on centers spaced substantially apart, said ports of one rotor being positioned in a one half of that particular rotor opposite from the one half of the other of said rotors containing said other rotors two ports.
  • sealing means is positioned in an annular recess around certain of said housing central portion ports, said recess opening axially endwise toward a radial surface of one of said rotors, said recess forming a radial annular end surface in said housing central portion axially spaced from said recess open end and a cylindrical annular wall from said recess end surface to said recess open end; and in which said sealing means includes a rigid annular sealing spool in said housing central portion recess axially movable along said recess cylindrical wall and axially abutting said rotor radial surface, a resilient sealing ring in said recess axially adjacent said sealing spool, a rigid annular backing spool in said recess axially movable along said recess cylindrical wall and axially adjacent said sealing ring, said backing spool having a radially reduced section extending axially along an inner side of said sealing ring confining
  • sealing means isposition ed in an annular recess around certain of said housing central portion ports, said recess opening axially endwise toward a rotor radial surface, said housing central portion recess forming a radial annular end surface in said housing central portion axially spaced from said recess open end and a cylindrical annular wall from said recess end surface to said recess open end; and in which said sealing means includes a rigid annular sealing spool in said housing central portion recess, said sealing spool having a main section axially movable along said recess cylindrical wall axially spaced from said recess end surface and axially abutting said rotor radial surface, said sealing spool having a radially reduced section spaced radially inward of said recess cylindrical wall extending axially from said main section to beyond said recess end surface within said housing central portion port and movable radially adjacent said recess end surface,
  • a rotary valve as defined in claim 1 in which said housing central portion and said rotors are constructed and said poi ts thereof arranged so that said rotors each totally cover one of said housing central portion ports during an interval of pivoting of said rotors between their two positions; and in which sealing means is positioned between certain of said housing central portion ports and each of said rotors for providing a fluid seal between said housing central portion and said rotors while permitting said pivotal movements of said rotors by said positioning rneans.
  • a rotary valve the combination of: a housing having spaced pressure chambers formed therein with a portion of said housing therebetween; a rotor pivotal between certain positions in each of said pressure chambers adjacent said housing portion; at least three ports through said housing por tion and opening into each of said spaced pressure chambers against said chamber rotors; at least two ports through each of said chamber rotors located alignable with certain of said housing portion ports in certain of said positions of said rotors forming communications between said certain housing portion ports and said chambers during said alignment; and positioning means for pivoting said chamber rotors between said certain positions.
  • a rotary valve as defined in claim 14 in which said two rotor ports are positioned relative to said three housing portion ports so that said two rotor ports of each rotor are alignable with a different combination of said housing portion ports in each of two positions of a particular rotor, each of said rotors sealing off all three of its housing portion ports during a part of said rotor pivoting between said rotor two positions.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Multiple-Way Valves (AREA)

Abstract

A housing has upper and lower pressure chambers separated by a housing central portion, each chamber containing a pivotal rotor adjacent the central portion. The housing central portion has first and second ports, each opening into both chambers against the rotors, a third port opening only into the upper chamber and a fourth port opening only into the lower chamber. Each rotor has two ports therethrough so that in alternate positions, the upper rotor ports communicate with the central portion third port and alternately with the central portion first and second ports, while the lower rotor ports communicate with the central portion fourth port and alternately with the central portion second and first ports. The rotors are connected simultaneously pivotal and spool seals are mounted in the ends of the central portion ports against the rotors permitting such rotor pivoting.

Description

United States Patent 5/l883 Wilson 1.990.423 2/ l 935 Bohneblust ABSTRACT: A housing has upper and lower pressure chambers separated by a housing central portion, each chamber containing a pivotal rotor adjacent the central portion. The housing central portion has first and second ports, each opening into both chambers against the rotors, a third port opening only into the upper chamber and a fourth port opening only into the lower chamber. Each rotor has two ports therethrough so that in alternate positions, the upper rotor ports communicate with the central portion third port and alternately with the central portion first and second ports, while the lower rotor ports communicate with the central portion fourth port and alternately with the central portion second and first ports. The rotors are connected simultaneously pivotal and spool seals are mounted in the ends of the central portion ports against the rotors permitting such rotor pivoting.
ROTARY VALVE AND IMPROVED FLUID SEALS NONINTERFLOW BACKGROUND or THE INVENTION v twopressure chambers, each having a flow controlling rotor therein, said chambersand rotors being constructed such that it is unnecessary to either increase the valve size or reduce the valve port size in order to obtain optimum noninterflow characteristics. As an added feature of the present invention, unique forms of spool-type seals are provided in the rotary valve between ports of a stationary valve housing and the pivotal valve rotors, again increasing the valve noninterflow characteristics made possible by the foregoing dual pressure chamber concept;
. In modern technology and industry, it has been along sought aftergoal to provide a rotary valve having controlled dual fluid stream flow therethrough with true noninterflow characteristics, yet without increasing the valve size or reducing the flow capacity thereof appreciably from prior rotary valves not having such noninterflow characteristics. As an example, assume'a rotary valve having an inlet port and an outlet port along with two separate working ports and his desired to alternate the fluid flow of two fluid streams, one entering the inlet port and the other exiting the outlet port, between the two working ports, that is, in one valve position, the inlet port would be connected to the first working port and the outlet port would be connected to the second working port, while in another valve position, the inlet port would be connected to the second working port and the outlet port would be connected to the first working port. Furthermore, assume that during a particular valve position, it is desired to provide minimum interrnixing between the two fluid flow streams and more important, to minimize such stream interrnixing, as well as minimize fluid pressure loss within the valve, during the valve movement between its two positions. i
An application forsuch a noninterflow valve might'be for the controlling of pressure fluid inlet and exhaust to and from a double acting, fluid actuated cylinder necessary to act in its opposite stroke movements in a very precise and exact, predetermined manner, without any appreciable variation. In such application, the rotary valve working ports would be con nected to the opposite ends of the fluid cylinder with the rotary valve alternate positioning alternately supplying fluid to and exhausting fluid from the cylinder ends. If the rotary valve controlling the fluid cylinder does not have excellent noninterflow characteristics, intermixing of the fluid flow streams or pressure losses within the valve can result in the movements of the fluid cylinder being erratic and unpredictable.
Prior to the present invention, where noninterflow characteristics are of importance, the problem has been satisfied by either making use of two separate rotary valves for the single application or greatly increasing the size of a single rotary valve. In the case of the two separate rotary valves, each can be of sufficient size and capacity so that the various ports thereof maybe separated sufiicient distances that the controlling movable rotors will completely close ports previously communicated with prior to opening other ports for the al-.
ternate fluid flow streams therethrough. in the case of a single rotary valve, the prior constructions have been increased in size for the same purpose, that is, to separate the various ports thereof sufficiently that the single movable rotor may move the rotor ports completely away from those ports previously communicated therewith to close the same prior to establishing communication with other ports to alternate the flow streams in the manner discussed.
t, Another required characteristic ofnoninterflow rotary valves important of consideration where absolute optimum noninterflow characteristics are desired is the construction of fluid seals between the ports of the stationary rotary valve housing and the ports of the pivotal rotors thereof. if interflow between the fluid streams is to be reduced to an absolute minimum so as to be virtually eliminated, particularly under high fluid pressure conditions, such seals must have excellent sealing characteristics, while still permitting the relative movement between the valve housings and rotors. Prior to the present invention, the sealing characteristics of the rotary valve seals have been quite lacking and troublesome, either engaging the valve parts with such high force so as to make the valve movements extremely difficult or engaging the valve partswith such a minimum force that fluid interflow is not prevented.
OBJECTS AND SUMMARY or THE INVENTION 1. It is, therefore, an object of this invention to provide a rotary valve adapted for simultaneously transmitting two fluid flow streams there'through and switching said streams between various thereof ,wherein stream interflow within said valve and pressure loss of said streams is greatly minimized, if not virtually completelyeliminated. The basic concept of the valve includes the provision of a single stationary housing portion between two separate pressure chambers, each chamber having a separate controlling rotor therein. The housing and rotor ports directing the separate fluid streams through the valve are arranged so that only one fluid stream flows through each of the pressure chambers in a given position of the valve, alternate positioning of the valve either redirecting each of said fluid streams through the same pressure chambers or, more preferably, switching the direction of individual stream flow to the other pressure chamber.
It is a further object of this invention to provide a rotary valve having the foregoing general characteristics and can struction wherein the valve stationary housing may be provided with a single pressure or inlet port through which there is always fluid inflow, a single exhaust or outlet port from which there is always fluid outflow, and two working ports which are alternately fluid inflow and outflow ports, said latter two working ports being those connected to a working mechanism controlled by the rotary valve. Further in the preferred form, the inlet and outlet ports of the rotary valve are connected to each of the pressure chambers and the two working ports are connected to one each of the pressure chambers. The individual rotors may. have the ports thereof arranged so that movement of. that particular rotor to one position will connect its connected working port to either the inlet or outlet port, and in another rotor position will connect its connected working port to the other of the inlet and outlet ports. Thus, by providing proper relative positioning between the two rotors of the two pressure chambers, it is possible to direct separate fluid streams separately through the pressure chambers in one position of the rotary valve and switch the direction of each fluid stream to the other or opposite of the pressure chambers in another position of the rotary valve.
It is still a further object of this invention to provide a rotary valve having true noninterflow characteristics without the necessity of increasing the valve size for a given flow capacity, or without the necessity of reducing the valve port size to thereby reduce the flow capacity thereof for a given overall valve size. By the use of two separate pressure chambers, each having a flow controlling rotor therein, said separate pressure chambers being arranged spaced about a single port containing stationary valve housing, it is possible to provide suflicient housing and rotor port spacing and separation so that at least certain of the ports may be completely closed prior to reopening or opening other ports between alternate positions of the valve. in this manner, fluid flow through the ports is completely blocked by the rotors to not only effectively prevent fluid stream interflow, but also to prevent pressure drops in the fluid streams normally resulting from such interflow and other fluid leakage. Again in the preferred form of the rotary valve, the two rotors for the pressure chambers are preferably simultaneously movable and the relative locations of the housing and rotor ports are such that all housing ports are effectively blocked for an interval between flow communicating positions of the rotors, resulting in maximum noninterflow characteristics despite the simultaneous fluid flow control of two fluid streams through the rotary valve.
It is an additional object of this invention to provide a rotary valve which may include parts or all of the foregoing advantageous characteristics and construction, and may further include unique forms of spool-type seals engaged between the valve stationary housing and the valve rotors producing extremely effective fluid seals for optimum noninterflow characteristics while still permitting ease of pivotal movement and positioning of the valve rotors. In the preferred form of the rotary valve of the present invention, the spool-type seals are preferably mounted in annular recesses surrounding the stationary housing ports urged axially into abutment with radial surfaces of the rotors and having resilient sealing rings arranged therein for maximum scaling in particular directions of fluid flow dependent on the more important fluid flow direction to or from that particular port. The unique spooltype seals included in the preferred form of rotary valve of the pr :sent invention may also have advantageous use and application in various other types of valves and fluid flow devices wherein fluid flow streams are directed between ports of adjacent members, and particularly where it is necessary to provide relative movement between said members while maintaining said port sealing Other objects and advantages of the invention will be apparent from the following specification and the accompanying drawings which are for the purpose of illustration only.
BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a preferred embodiment of a rotary valve incorporating the principles of the present invention;
FIG. 2 is an enlarged, vertical sectional view looking in the direction of the arrows 2-2 in FIG. 1;
FIG. 3 is an enlarged, fragmentary, vertical sectional view taken from FIG. 2 and showing one form of spool-type seal of the present invention;
FIG. 4 is a view similar to FIG. 3 but showing another form of spool-type seal of the present invention;
FIG. 5 is a reduced, horizontal sectional view looking in the direction of the arrows 5-5 in FIG. 2;
FIG. 6 is a reduced, horizontal sectional view looking in the direction of the arrows 6-6 in FIG. 2;
FIG. 7 is a reduced, horizontal sectional view looking in the direction of the arrows 7-7 in FIG. 2;
FIG. 8 is a reduced, horizontal sectional view looking in the direction of the arrows 8-8 in FIG. 2; and
FIG. 9 is a fragmentary, vertical sectional view looking in the direction of the arrows 9-9 in FIG. 2 and showing certain of the valve housing fluid flow ports in hidden lines and certain other of said housing ports in phantom lines to illustrate the relative positioning thereof.
A preferred embodiment of rotary valve including the principles of the present invention is shown in the drawings and includes a generally cylindrical, stationary housing generally indicated at It) formed by a central housing portion l2 axially spacing or separating upper and lower housing portions 14 and 16, all of said housing portions preferably being formed of stainless steel or the like with the upper and lower housing portions being secured to the central housing portion by a series of appropriate fasteners 18. Generally cylindrical pressure chambers 20 and 22 are formed in the upper and lower housing portions 14 and 16, the upper pressure chamber being substantially identical to the lower pressure chamber except axially reverse and each being enclosed by its respective upper or lower housing portion with the exception of opening axially against the central housing portion 12. A centrally located positioning shaft 24 is received axially through the central housing portion 12 extending downwardly into the lower pressure chamber 22 and upwardly through both of the upper pressure chamber 20 and the upper housing portion 14.
A generally cylindrical upper rotor 26 is positioned in the upper pressure chamber 20 substantially radially spanning said upper pressure chamber with a lower surface 28 thereof axially adjacent the central housing portion 12, and a similar lower rotor 30 is similarly positioned in the lower pressure chamber 22 with an upper surface 32 adjacent the central housing portion. The upper and lower rotors 26 and 30 receive the positioning shaft 24 axially therethrough and are appropriately keyed to the positioning shaft for rotatable or pivotal movement therewith. Furthermore, thrust bearings 34 are mounted in the central housing portion 12 axially abutting the upper rotor lower surface 28 and the lower rotor upper surface 32, the upper rotor 26 being retained downwardly against the upper of the thrust bearings 34 by a shaft collar 36 and the lower rotor 30 being retained upwardly against the lower of the thrust bearings 34 by a nut 38 on the lower end of the positioning shaft 24.
Resilient sealing O-rings 44 are positioned surrounding the positioning shaft 24 at the upper and lower extremities of the central housing portion 12 sealing radially between said shaft and central housing portion preventing fluid flow axially along the positioningshaft between the upper and lower pressure chambers 20 and 22 while still permitting rotation of the positioning shaft relative to the central housing portion. Further, a
similar sealing Q-ring 46 is positioned around the positioning shaft 24 upwardly of the upper pressure chamber 20 and the shaft collar 36 sealing radially between the positioning shaft and the upper housing portion 14 preventing fluid flow axially along the positioning shaft and upwardly through the upper housing portion 14. Still further, similar sealing O-ririgs 48 are positioned around the central housing portion I2 above and below the thrust bearings 34 between the central housing portion and the upper and lower housing portions 14 and I6 preventing fluid flow from the upper and lower pressure chambers 20 and 22 between these housing portions.
Generally opposite first and second housing ports 50 and 52 are formed through the central housing portion 12, each communicating with both of the upper and lower pressure chambers 20 and 22 as will be hereinafter explained more in detail. Also, generally opposite third and fourth housing ports 54 and 56, spaced alternately between the first and second housing ports 50 and 52, are formed through the central housing portion 12, the third housing port communicating with only the upper pressure chamber 20 and the fourth housing port communicating with only the lower pressure chamber 22. All of the first through fourth housing ports 50, 52, 54 and 56 open into the respective upper and lower pressure chambers 20 and 22 axially toward and against the upper and lower rotors 26 and 30 so that the rotors are positioned for controlling fluid flow through these housing ports, depending on the particular positioning of the rotors.
As best seen in FIGS. 6, 7 and 9, the first housing port 50 includes a primary part 58 extending radially into the central housing portion 12 and connected secondary upper and lower parts 60 and 62 extending axially through said central housing portion and respectively to the upper and lower pressure chambers 20 and 22, the second housing port 52 including the similarly extending primary part 64, secondary upper part 66 and secondary lower part 68 Furthermore, as best determined by a comparison of FIGS. 6 and 7, the secondary upper and lower parts 60 and 62 of the first housing port 50 are circumferentially offset or at opposite circumferential sides of and communicating with the primary part 58 of said first housing port, while the secondary upper and lower parts 66 and 68 of the second housing port 52 are similarly circumferentially offset at opposite citcumferential sides of the primary part 64 of said second housing port. As shown in FIG. 9, the secondary upper parts 60 and 66 of the first and second housing ports 50 and 52 are shown in phantom lines and the secondary lower parts 62 and 68 thereof are shown in broken lines to indicate such relative circumferential offset positioning. The result is that the center lines of the secondary upper parts 60 and 66 of the first and second housing ports 50 and 52 are circumferentially spaced l communicating with common sides of the primary parts 58 and 64 of said housing ports asviewed in FIG. 6, and the center lines of the secondary. lower parts 62 and 68 of the first and second housing ports 50 and 52 are spaced apart 120 in the opposite circumferential direction and communicate with the opposite sides of the primary parts 58 and 64 of said housing ports as viewed in FIG. 7.
The third housing port 54 extends radially and then axially to the upper pressure chamber20 on right angle coincident center lines as best seen in FIGS. 2 and 6, the fourthhousing port 56 extending similarly to the lower pressure chamber 22 as best seen in FIGS. 2 and 7. The further result, therefore, is that the third housing port 54 opens into the upper pressure chamber 20 with the center line thereof spaced 120 between the center lines of the first and second housing ports 50 and-52 as shown in FIG. 6, while the fourth housing port 56 opens into the lower pressure chamber. 22 with the center line thereof ofiset 120 between the center lines of the first and second housing ports 50 and 52 as shownin FIG. 7. Thus, the first, second and third housing ports 50, 52 and 54 open axially into the upper pressure chamber ZO'againstthe upper rotor 26 substantially equally circumferentially spaced about the central housing portion 12, and the first, second and fourth housing ports 50, 52 and 56 open axially into the lower pressure chamber 22 against the lower rotor equally circumferentially spaced about the central housing portion 12 but circumferentially between said port openings into the upper pressure chamber.
As shown in FIG. 5, the upper rotor 26 has two ports 70 formed axially therethrough withthe center lines of said ports being spaced apart. l20, and as shown in FIG. 8, the lower rotor 30 has two ports 72 formed axially therethrough with the center lines of said ports spaced 120 apart. The upperrotor ports 70 may therefore be positioned alternately in communication with the first and third housing ports 50 and 54 or the second and third housing ports 52'and 54, and the lower rotor ports 72 may be positioned in communication alternately with the first and fourth housing ports 50 and 56 or the second and fourth housing ports 52 and 56. Equally important, however, not only are the upper and lower rotors 26 and 30 simultaneously pivotal by pivoting the positioning shaft 24, but the the upper rotor ports 70 are in the opposite circumferential half of the upper rotor from the lower rotor ports 72 in the lower rotor.
The various ports of the central housing portion 12 and the upper and lower rotors 26 and 30 are therefore positioned in relation to each other so that the upper pressure chamber 20 can only communicate one at a time with the first and second housing ports 50 and 52 and the lower pressure chamber 22 can only communicate one at a time with said first and second housing ports. Furthermore, when the upper pressure chamber 20 is in communication with the first housing port 50, the lower pressure chamber 22 is in communication with the second housing portion 52, and when the upper pressure chamber is in communication with the second housing port, the lower pressure chamber is in communication with the first housing port, the two pressure chambers never being in communication with the same of the first and second housing ports in the particular arrangement shown. It will also be noted that the 120 circumferential spacing of the center lines of both the housing and rotor ports taken with the relative sizes of said ports permit all housing ports to be closed by the upper and lower rotors 26 and 30 duringan interval in the movement of said rotors between their alternate communicating positions.
As best seen in FIGS. 1, 2 and 9, the positioning shaft 24 projects upwardly through the upper housing portion 14 with the upper end thereof telescoped by a positioning cap 74 pivotally overlying the upper housing portion. The positioning cap 74 is secured to the positioning shaft 24 by a connecting pin 76, whereby, pivotal movement of the positioning cap causes consequent pivotal movement of the positioning shaft for pivoting the upper and lower rotors 26 and 30 between their alternate positions in the manner hereinbefore described. Such alternate positions of the upper and lower rotors 26 and 30 is preferably determined by a positioning pin 78 mounted in the upper housing portion 14 and projecting upwardly into an arcuate positioning slot80 formed in and opening downwardly of the positioning cap 74, the extremities of the positioning slot determining the upper and lower rotor alternate positions. In addition, it is preferred to provide a spring urged positioning ball 82 mounted in the upper housing portion 14 for upward reception in a series of spaced, arcuate, positioning recesses 84 in and opening downwardly of the positioning cap 74, the positioning recesses being appropriately spaced for determining the various positions of the upper and lower rotors. I
Referring particularly to FIGS. 3 and 4, in order to provide optimum noninterflow characteristics of the rotary valve of the present invention, unique forms of spool-type seals are arranged in the various first, second, third and fourth housing ports 50, 52, 54 and 56 at the ends of these ports against the upper and lower rotors 26 and 30. The spool-type seal of FIG. 3 is preferably mounted in each of the first, third and fourth housing ports 50, 54 and 56, said seal being arranged for providing maximum sealing qualities when fluid is flowing 1 from that particular housing port toward the upper'or lower rotor 26 or 30 and toward the upper or lower pressure chamber 20 or 22, although a certain amount of sealing is provided by this seal for fluid flow in the reversedirection. The seal of FIG. 4 is mounted in each of the two second housing ports 52 and is particularly adapted for sealing fluid where fluid flow is from the upper or lower pressure chamber 20 or 22 through the upper or'lower rotor 26' or 30 into the central housing portion 12 since the fluid flow in these second housing ports 52 will always be in this direction in a particular embodiment of rotary valve shown.
Referring more particularly to FIG. 3, a spool-type seal generally indicated at 86 is received in an annular recess generally indicated at 88 of the central housing portion 12 surrounding the end of one branch of the first housing port 50, said recess 88 opening axially endwise toward, in this particular case, the lower radial surface 29 of the upper rotor 26 and forming a radial annular end surface 90 axially spaced from the recess open end and a cylindrical annular wall 92 extending axially from said end surface 90 to the recess open end. As shown, the recess 88 also preferably includes an auxiliary recess portion 94 radially outwardly offset form the main part of recess 88 at the open end of the first port 50 in the central housing portion 12. The auxiliary recess portion 94 is likewise annular opening radially into the first housing port 50 forming a part of the recess cylindrical wall 97. and opening endwise toward the upper rotor 26.
The seal 86 includes rigid, annular sealing spool 96 axially movable, preferably slidable, along the recess cylindrical wall 92 with an annular, reduced radial section 98 axially aligned with and axially movable in the auxiliary recess portion 94. Furthermore, the reduced radial section 98 of the sealing spool 96 axially abuts the lower radial surface 28 of the upper rotor 26 while forming a relieved end surface I00 around the sealing spool 96. The sealing spool 96 terminates axially away from the upper rotor 26 within the recess 88 axially spaced from the recess end surface 90.
The seal 86 further includes an annular, preferably radially flat, guard ring 102 in the recess 88 axially adjacent the sealing spool 96, a resilient sealing ring 104 in the recess axially adjacent the guard ring, a rigid, annular backing spool 106 in the recess axially adjacent the sealing ring 104, and an annular spring 108 in the recess axially between the backing spool and the recess end surface 90. The backing spool 106 is axially movable, preferably slidable, along the recess cylindrical wall 92 and has a radially reduced section 110 extending radially inwardly of and axially along the sealing ring 1114 and the guard ring 102, movably telescoped by the sealing spool 96. The reduced section 110 of the backing spool 106, therefore, confines the guard ring 102 and sealing ring 104 between this reduced section and the recess Cylindrical wall 92 as shown.
The guard ring 102 closely slidably abuts the recess cylindrical wall 92 to prevent the sealing ring 104 from extruding axially along this guard ring and between the sealing spool es and the recess cylindrical wall upon the sealing ring being axially deformed or flattened by fluid flow pressure axially against said sealing ring from between the backing spool 1G6 and the recess cylindrical wall. At the same time, it is preferred to dimension the sealing ring 104 so that said sealing ring during said axial flattening will seal tightly against the recess cylindrical wall 92, while exerting lesser radial pressure against the radially reduced section 110 of the backing spool 106 permitting movement between said backing spool and the sealing spool 96.
The spring 108 is preferably a deformed, washer-type spring reacting axially between the backing spool 1116 and the recess end surface 90 while occupying a minimum axial space of the recess 88. As examples, the spring 108 may be formed of spring steel, and the sealing and backing spools 96 and 11% may be formed of stainless steel, metal being preferred partic ularly where high fluid pressures are involved. The guard ring 102 may be of plastic, such as one of the usual memory plastics, and the sealing ring 104 may be a usual resilient material O-ring.
Thus, with the seal 86 of FIG. 3 in the first, third and fourth housing ports 50, 54 and 56, fluid flow pressure around the backing spool 106 between said backing spool and the recess cylindrical wall 92 will axially flatten the sealing ring 1114 to seal between said sealing ring and said recess cylindrical wall. This said pressure will exert axial pressure against the sealing spool 96 to cause the reduced radial section 98 of the sealing 'spool to sealingly abut the particular radial surface of the upper or lower rotor 26 or 30. With the provision of the axially reacting spring 1015, such spring will augment this axial abutment, although the reduced radial section 28 of the sealing spool 96 will be somewhat axial balanced by fluid pressure against the relieved end surface 11111 of the sealing spool so that excess pivoting force is not required to pivot the rotors. Although maximum sealing of the seal $6 is obtained where the fluid flow pressure is in the axial direction from the particular housing port, it will be appreciated that a certain amount of sealing takes place even with the fluid flow in the reverse direction.
Referring particularly to FIG. 4, a seal generally indicated at 112 is mounted in a recess generally indicated at 116 at the ends of the second housing ports 52 in the central housing portion 12, the particular second housing port shown being that opening axially against the upper rotor 26. As hereinbefore pointed out, the fluid flow of the second housing ports 52 of the particular embodiment of rotary valve illustrated is always from the upper and lower pressure chambers 20 and 22 axially into said second housing ports so that the seal 112 is particularly adapted for such flow. The recess 114 is somewhat similar to that for the seal 86 and, in this case, is annular surrounding the ends of the second housing ports 52 opening axially toward the lower radial surface 28 of the upper rotor 26 forming an annular end surface 116 spaced axially from the upper rotor 26 and an annular, cylindrical wall 116 extending axially from said end surface to said open end.
The seal 112 includes a rigid, annular sealing spool 1211 having a main section 122 primarily within the recess 114i and movable, preferably slidable, axially along the recess cylindrical wall 118. The sealing spool main section 122 is axially spaced from the recess end surface 116 and has a reduced radial section 12d extending axially from said main section 122 axially past the recess end surface within the second housing port 52, although closely radially adjacent said end surface inner extremity as shown. The sealing spool 120 further has a reduced radial section 126 preferably axially aligned with the reduced radial section 124, but projecting axially from the main section 122 toward and abutting the lower surface 28 of the upper rotor 26 and forming a relieved end surface 128 on said sealing spoolmain section 122.
The seal 112 further includes an axially reacting spring 130 axially between the sealing spool main section 122 and the recess end surface 116, a rigid backup ring 132 axially adjacent said spring, a resilient sealing ring 134 axially adjacent said backup ring, and a guard ring 136 axially between said sealing ring and the recess end surface 116. All of the spring 130, backup ring 132, sealing ring 134 and guard ring 136 are radially confined by the sealing spool reduced radial section 124 between said reduced radial section and the recess cylindrical wall 118, the backup ring 132 being axially movable, preferably slidable, between said sealing spool reduced radial section 124 and the recess cylindrical wall 18 and the guard ring 136 at least closely slidably abutting the sealing spool reduced radial section 124. The sealing spool and backup ring may again be formed of stainless steel, the washer-type spring 1300f spring steel and the guard ring 136 of memory plastic, with the sealing ring 134 a usual O-ring.
With the seal 112 and the fluid flow pressure axially from the upper pressure chamber 20 into the second housing port 52, therefore, fluid pressure will be exerted outwardly around the sealing spool main section 122, the spring 130 and the backing ring 132 to axially flatten the sealing ring 134 which is preferably dimensioned to exert maximum radial pressure against the reduced radial section 124 of the sealing spool and lesser radial pressure against the recess cylindrical wall 118 permitting movement of the sealing spool 120 within the recess 114. The guard ring 136 prevents axial extrusion of the sealing ring 134 along the reduced radial section 124 of the sealing spool 120, and the spring acts axially against both the sealing spool main section 122 and the backup ring 132. The spring pressure axially against the sealing spool main section 122 forces the reduced radial section 126 into abutment with the upper rotor 26, while the relieved end surface 128 of the sealing spool 120 somewhat balances this axial sealing pressure permitting ease of movement of the rotors.
In operation of the particular embodiment of rotary valve illustrated, assume that the first housing port 50 is connected to a source of fluid under pressure for receiving fluid into the rotary valve, the second housing port 52 is connected back to said fluid source for directing exhaust fluid to said source, and the third and fourth housing ports 54 and 56 are connected to opposite ends of a double acting, fluid actuated cylinder. With the upper and lower rotors 26 and 30 in the positions shown in FIG. 5 and 8, the fluid will flow into and through the first housing port 50, upwardly through one of the upper rotor ports 70 into the upper pressure chamber 21), downwardly through the other of the upper rotor ports 70 into the third housing port 54, and through said third housing port to one end of the fluid cylinder driving the fluid cylinder in one direction. At the same time, fluid will exhaust from the opposite end of the fluid cylinder into and through the fourth housing port 56 downwardly through one of the lower rotor ports 72 into the lower pressure chamber 22, upwardly through the other of the lower rotor ports 72 into the second housing port 52, and through and from said second housing port ounvardly exhausting back to the source of fluid.
Pivoting the positioning shaft 24 to pivot the upper and lower rotors 26 and 30 simultaneously to their alternate positions will axially align the upper rotor ports 70 with the second and third housing ports 52 and $4, and the lower rotor ports 72 with the first and fourth housing ports 50 and 56, thereby reversing the fluid flow through the upper and lower pressure chambers 20 and 22, and reversing the fluid flow through the third and fourth housing ports 54 and 56. This reverses the direction of driving of the fluid cylinder and although the direction of fluid flow in the third and fourth housing ports 54 and 56 is reversed, the first housing port 50 remains an inlet port and the second housing port 52 remains an exhaust or ,L outlet port. Furthermore, in the, pivotal movement of the upper and lower rotors 26 and 30, it will be noted that all of the housing ports 50, 52, 54 and 56 of the central housing portion 12 are completely closed by the upper and lower rotors during an interval of such pivotal movement so as to prevent interflow between said ports and maintain pressure within the upper and lower. pressure chambers 20 and 22, the unique seals 86 and 112 augmenting this noninterflow characteristic and providing optimum results.
Thus, according to the principles of the present invention, a rotary valve is provided having a unique construction including two pressure chambers 20 and 22 incorporated in a minimumsize valve housing which permits the formation of a true, noninterflow rotary valve. The provision of the separate pressure chambers and 22 permits proper spacing of the various housing and rotor ports required for such interflow characteristics without the necessity of either increasing the overall rotary valve size or reducing the capacity thereof for a given valve size. Where optimum noninterflow characteristics are desired, and particularly where relatively high fluid pressures are encountered, unique forms of spool-type seals 96 and 112 are incorporated in the rotary valve providing maximum sealing while still permitting relative ease of rotary valve operation and switching between the various positions thereof, said unique seal constructions being advantageously usable in other fluid transmitting'devices and particularly where relatively movable members are encountered.
I claim:
1. In a rotary valve, the combination of: a housing including axially spaced upper and lower portions separated by a central portion; a pressure chamber formed in each of 'said housing upper and lower ortions opening axially against said housing central portion; a rotor pivotal between at least two positions in each of said upper and lower pressure chambers axially adjacent said housing central portiom spaced first, second, third and fourth ports through said housing central portion and into certain of said pressure chambers, said first and second ports opening into each of said pressure chambers against said rotors thereof, said third port opening into said upper pressure chamber against said upper chamber rotor and being free of opening into said lower pressure chamber, said fourth port openinginto said lower pressure chamber against said lower chamber rotor andbeing free of opening into said upper pressure chamber; two particularly positioned ports through each of said rotors communicating axially between said housing central portion and the respective of said pressure chambers,
\ said ports of said upper chamber rotor communicating through said upper chamber rotor and said upper pressure chamber between at least said first and third housing central portion ports when said upper chamber rotor is in one of said positions and between at least said second and third housing central portion ports when said upper chamber rotor is in the other of saidpositions, said ports of said lower chamber rotor communicating through said lower chamber rotor and said lower pressure chamber between at least said second and fourth housing central portion ports when said lower chamber rotor is in one of said positions and between at least said first and fourth housing central portion ports when said lower chamber rotor is in the other of said positions; and positioning means for pivoting said rotors between their two positions.
2. A rotary valve as defined in claim 1 in which said rotors and said housing central portion are constructed and said ports thereof respectively arranged so that each of said rotors seals off one of said ports of said housing central portion in each of said rotor positions.
3. A rotary valve as defined in claim 1 in which said positioning means is operably connected'to each of said rotors for simultaneously pivoting said rotors between each of said rotors two positions.
4. A rotary valve as defined in claim 1 in which said positioning means is operably connected to both of said rotors for simultaneously pivoting said rotors between each rotor two positions, said positioning'means operable connection placing both of said rotors simultaneously in their one position and simultaneously in their other position.
5. A rotary valve as defined in claim 1 in which each of said rotors is constructedand the ports thereof arranged sealing off at least one of said housing central portion ports previously communicating with at least one of said rotor ports prior to said at least one rotor ports communicating with another of said housing central portion ports during said pivotal movements of said rotors by said positioning; means.
6. A rotary valve as defined in claim 1 in which said rotors are constructed and said ports thereof arranged sealing off all of said housing central portion ports during an interval of rotorpivotal movement by said positioning means between said rotor two positions.
7. A rotary valve as defined in claim 1 in which said rotor positioning means includes a shaft extending axially through said housing central portion pivotal relative to said housing central portion and secured to each of said rotors for simultaneously pivoting said rotors during pivotal movement of said shaft.
8. A rotary valve as defined in claim 1 in which annular sealing means is positioned in certain of said housing central portion ports resiliently urged abutting radial surfaces of said rotor for forming a fluid seal axially between said housing central portion and said rotors while permitting pivotal movements of said rotors relative to said housing central portion by said rotor positioning means.
9. A rotary valve as defined in claim 1 in which each of said rotors is constructed and said ports thereof arranged for pivotal movement of said rotors through substantially l20 between said rotor two positions.
10. A rotary valve as defined in claim 1 in which said rotor positioning means is operably connected to said rotors for simultaneously pivoting said rotors between said rotor two positions, said rotors each being in said one position simultaneously and in, said other position simultaneously; and in which said two ports of each rotor are on centers spaced substantially apart, said ports of one rotor being positioned in a one half of that particular rotor opposite from the one half of the other of said rotors containing said other rotors two ports.
11. A rotary valve as defined in claim 1 in which sealing means is positioned in an annular recess around certain of said housing central portion ports, said recess opening axially endwise toward a radial surface of one of said rotors, said recess forming a radial annular end surface in said housing central portion axially spaced from said recess open end and a cylindrical annular wall from said recess end surface to said recess open end; and in which said sealing means includes a rigid annular sealing spool in said housing central portion recess axially movable along said recess cylindrical wall and axially abutting said rotor radial surface, a resilient sealing ring in said recess axially adjacent said sealing spool, a rigid annular backing spool in said recess axially movable along said recess cylindrical wall and axially adjacent said sealing ring, said backing spool having a radially reduced section extending axially along an inner side of said sealing ring confining said sealing ring radially between said reducedsection and said recess cylindrical wall, said reduced section being movably telescoped by said sealing spool, fluid under pressure flowing from said housing central portion port to a rotor port exerting axial pressure against said backing spool and sealing ring to axially flatten said sealing ring sealing against said recess cylindrical wall and force said sealing spool axially against said rotor radial surface.
12. A rotary valve as defined in claim 1 in which sealing means isposition ed in an annular recess around certain of said housing central portion ports, said recess opening axially endwise toward a rotor radial surface, said housing central portion recess forming a radial annular end surface in said housing central portion axially spaced from said recess open end and a cylindrical annular wall from said recess end surface to said recess open end; and in which said sealing means includes a rigid annular sealing spool in said housing central portion recess, said sealing spool having a main section axially movable along said recess cylindrical wall axially spaced from said recess end surface and axially abutting said rotor radial surface, said sealing spool having a radially reduced section spaced radially inward of said recess cylindrical wall extending axially from said main section to beyond said recess end surface within said housing central portion port and movable radially adjacent said recess end surface, axially reacting spring means axially adjacent said sealing spool main section radially confined between said sealing spool reduced section and said recess cylindrical wall, a rigid backup ring axially adjacent said spring means and axially movable along and radially between said sealing spool reduced section and said recess cylindrical wall, a resilient sealing ring axially between said backup ring and said recess end surface radially confined between said sealing spool reduced section and said recess cylindrical wall, the combination of said spring means reacting axially between said sealing spool and backup ring and fluid under pressure flowing through said housing central portion port urging said sealing spool axially against said rotor radial surface and axially flattening said sealing ring to seal against said recess cylindrical wall.
13. A rotary valve as defined in claim 1 in which said housing central portion and said rotors are constructed and said poi ts thereof arranged so that said rotors each totally cover one of said housing central portion ports during an interval of pivoting of said rotors between their two positions; and in which sealing means is positioned between certain of said housing central portion ports and each of said rotors for providing a fluid seal between said housing central portion and said rotors while permitting said pivotal movements of said rotors by said positioning rneans.
14. In a rotary valve, the combination of: a housing having spaced pressure chambers formed therein with a portion of said housing therebetween; a rotor pivotal between certain positions in each of said pressure chambers adjacent said housing portion; at least three ports through said housing por tion and opening into each of said spaced pressure chambers against said chamber rotors; at least two ports through each of said chamber rotors located alignable with certain of said housing portion ports in certain of said positions of said rotors forming communications between said certain housing portion ports and said chambers during said alignment; and positioning means for pivoting said chamber rotors between said certain positions.
15. A rotary valve as defined in claim 14 in which said two rotor ports are positioned relative to said three housing portion ports so that said two rotor ports of each rotor are alignable with a different combination of said housing portion ports in each of two positions of a particular rotor, each of said rotors sealing off all three of its housing portion ports during a part of said rotor pivoting between said rotor two positions.

Claims (15)

1. In a rotary valve, the combination of: a housing including axially spaced upper and lower portions separated by a central portion; a pressure chamber formed in each of said housing upper and lower portions opening axially against said housing central portion; a rotor pivotal between at least two positions in each of said upper and lower pressure chambers axially adjacent said housing central portion; spaced first, second, third and fourth ports through said housing central portion and into certain of said pressure chambers, said first and second ports opening into each of said pressure chambers against said rotors thereof, said third port opening into said upper pressure chamber against said upper chamber rotor and being free of opening into said lower pressure chamber, said fourth port opening into said lower pressure chamber against said lower chamber rotor and being free of opening into said upper pressure chamber; two particularly positioned ports through each of said rotors communicating axially between said housing central portion and the respective of said pressure chambers, said ports of said upper chamber rotor communicating through said upper chamber rotor and said upper pressure chamber between at least said first and third housing central portion ports when said upper chamber rotor is in one of said positions and between at least said second and third housing central portion ports when said upper chamber rotor is in the other of said positions, said ports of said lower chamber rotor communicating through said lower chamber rotor and said lower pressure chamber between at least said second and fourth housing central portion ports when said lower chamber rotor is in one of said positions and between at least said first and fourth housing central portion ports when said lower chamber rotor is in the other of said positions; and positioning means for pivoting said rotors between their two positions.
2. A rotary valve as defined in claim 1 in which said rotors and said housing central portion are constructed and said ports thereof respectively arranged so that each of said rotors seals off one of said ports of said housing central portion in each of said rotor positions.
3. A rotary valve as defined in claim 1 in which said positioning means is operably connected to each of said rotors for simultaneously pivoting said rotors between each of said rotors two positions.
4. A rotary valve as defined in claim 1 in which said positioning means is operably connected to both of said rotors for simultaneously pivoting said rotors between each rotor two positions, said positioning means operable connection placing both of said rotors simultaneously in their one position and simultaneously in their other position.
5. A rotary valve as defined in claim 1 in which each of said rotors is constructed anD the ports thereof arranged sealing off at least one of said housing central portion ports previously communicating with at least one of said rotor ports prior to said at least one rotor ports communicating with another of said housing central portion ports during said pivotal movements of said rotors by said positioning means.
6. A rotary valve as defined in claim 1 in which said rotors are constructed and said ports thereof arranged sealing off all of said housing central portion ports during an interval of rotor pivotal movement by said positioning means between said rotor two positions.
7. A rotary valve as defined in claim 1 in which said rotor positioning means includes a shaft extending axially through said housing central portion pivotal relative to said housing central portion and secured to each of said rotors for simultaneously pivoting said rotors during pivotal movement of said shaft.
8. A rotary valve as defined in claim 1 in which annular sealing means is positioned in certain of said housing central portion ports resiliently urged abutting radial surfaces of said rotor for forming a fluid seal axially between said housing central portion and said rotors while permitting pivotal movements of said rotors relative to said housing central portion by said rotor positioning means.
9. A rotary valve as defined in claim 1 in which each of said rotors is constructed and said ports thereof arranged for pivotal movement of said rotors through substantially 120* between said rotor two positions.
10. A rotary valve as defined in claim 1 in which said rotor positioning means is operably connected to said rotors for simultaneously pivoting said rotors between said rotor two positions, said rotors each being in said one position simultaneously and in said other position simultaneously; and in which said two ports of each rotor are on centers spaced substantially 120* apart, said ports of one rotor being positioned in a one half of that particular rotor opposite from the one half of the other of said rotors containing said other rotors two ports.
11. A rotary valve as defined in claim 1 in which sealing means is positioned in an annular recess around certain of said housing central portion ports, said recess opening axially endwise toward a radial surface of one of said rotors, said recess forming a radial annular end surface in said housing central portion axially spaced from said recess open end and a cylindrical annular wall from said recess end surface to said recess open end; and in which said sealing means includes a rigid annular sealing spool in said housing central portion recess axially movable along said recess cylindrical wall and axially abutting said rotor radial surface, a resilient sealing ring in said recess axially adjacent said sealing spool, a rigid annular backing spool in said recess axially movable along said recess cylindrical wall and axially adjacent said sealing ring, said backing spool having a radially reduced section extending axially along an inner side of said sealing ring confining said sealing ring radially between said reduced section and said recess cylindrical wall, said reduced section being movably telescoped by said sealing spool, fluid under pressure flowing from said housing central portion port to a rotor port exerting axial pressure against said backing spool and sealing ring to axially flatten said sealing ring sealing against said recess cylindrical wall and force said sealing spool axially against said rotor radial surface.
12. A rotary valve as defined in claim 1 in which sealing means is positioned in an annular recess around certain of said housing central portion ports, said recess opening axially endwise toward a rotor radial surface, said housing central portion recess forming a radial annular end surface in said housing central portion axially spaced from said recess open end and a cylindrical annular wall from said recess end surface to said recess open end; and in which Said sealing means includes a rigid annular sealing spool in said housing central portion recess, said sealing spool having a main section axially movable along said recess cylindrical wall axially spaced from said recess end surface and axially abutting said rotor radial surface, said sealing spool having a radially reduced section spaced radially inward of said recess cylindrical wall extending axially from said main section to beyond said recess end surface within said housing central portion port and movable radially adjacent said recess end surface, axially reacting spring means axially adjacent said sealing spool main section radially confined between said sealing spool reduced section and said recess cylindrical wall, a rigid backup ring axially adjacent said spring means and axially movable along and radially between said sealing spool reduced section and said recess cylindrical wall, a resilient sealing ring axially between said backup ring and said recess end surface radially confined between said sealing spool reduced section and said recess cylindrical wall, the combination of said spring means reacting axially between said sealing spool and backup ring and fluid under pressure flowing through said housing central portion port urging said sealing spool axially against said rotor radial surface and axially flattening said sealing ring to seal against said recess cylindrical wall.
13. A rotary valve as defined in claim 1 in which said housing central portion and said rotors are constructed and said ports thereof arranged so that said rotors each totally cover one of said housing central portion ports during an interval of pivoting of said rotors between their two positions; and in which sealing means is positioned between certain of said housing central portion ports and each of said rotors for providing a fluid seal between said housing central portion and said rotors while permitting said pivotal movements of said rotors by said positioning means.
14. In a rotary valve, the combination of: a housing having spaced pressure chambers formed therein with a portion of said housing therebetween; a rotor pivotal between certain positions in each of said pressure chambers adjacent said housing portion; at least three ports through said housing portion and opening into each of said spaced pressure chambers against said chamber rotors; at least two ports through each of said chamber rotors located alignable with certain of said housing portion ports in certain of said positions of said rotors forming communications between said certain housing portion ports and said chambers during said alignment; and positioning means for pivoting said chamber rotors between said certain positions.
15. A rotary valve as defined in claim 14 in which said two rotor ports are positioned relative to said three housing portion ports so that said two rotor ports of each rotor are alignable with a different combination of said housing portion ports in each of two positions of a particular rotor, each of said rotors sealing off all three of its housing portion ports during a part of said rotor pivoting between said rotor two positions.
US3561479D 1968-08-12 1968-08-12 Noninterflow rotary valve and improved fluid seals Expired - Lifetime US3561479A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0052743A1 (en) * 1980-11-24 1982-06-02 RUBINETTERIE STELLA S.p.A. Seal for fluid intake ports in single lever mixer faucets
US5651555A (en) * 1995-11-13 1997-07-29 Barksdale, Inc. Fluid-operated leveling valve systems
CN105202225A (en) * 2014-06-10 2015-12-30 克拉玛依市金牛信泰石油设备有限公司 Valve base ring and multi-way valve with same
US10040331B2 (en) 2016-04-04 2018-08-07 Barksdale Inc. Ride height leveling with selectable configurations system and method
JPWO2022220078A1 (en) * 2021-04-13 2022-10-20

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US278648A (en) * 1883-05-29 Balanced rotary valve
US1990423A (en) * 1933-08-26 1935-02-05 Bohnenblust Ben Valve

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US278648A (en) * 1883-05-29 Balanced rotary valve
US1990423A (en) * 1933-08-26 1935-02-05 Bohnenblust Ben Valve

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0052743A1 (en) * 1980-11-24 1982-06-02 RUBINETTERIE STELLA S.p.A. Seal for fluid intake ports in single lever mixer faucets
US5651555A (en) * 1995-11-13 1997-07-29 Barksdale, Inc. Fluid-operated leveling valve systems
CN105202225A (en) * 2014-06-10 2015-12-30 克拉玛依市金牛信泰石油设备有限公司 Valve base ring and multi-way valve with same
CN105202225B (en) * 2014-06-10 2017-12-22 克拉玛依市金牛信泰石油设备有限公司 Valve cup ring and the banked direction control valves with the valve cup ring
US10040331B2 (en) 2016-04-04 2018-08-07 Barksdale Inc. Ride height leveling with selectable configurations system and method
US10479159B2 (en) 2016-04-04 2019-11-19 Barksdale, Inc. Ride height leveling with selectable configurations: system and method
JPWO2022220078A1 (en) * 2021-04-13 2022-10-20
WO2022220078A1 (en) * 2021-04-13 2022-10-20 イーグル工業株式会社 Selector valve

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