Title of Invention

A SELECTOR FLUID CONTROL VALVE

Abstract A high-pressure primary fluid control valve and a multi-pressure selector fluid control valve are disclosed for operating a fluid- actuated device. Preferably a spherical ball-poppet and frusto-conical valve seat adapted for substantially line-contact therebetween are provided with an upstream flow area adjacent the line-contact in order to substantially minimize sonic flow damage to the actual sealing surface of the valve seat by shifting it away from such line-contact seating. Preferably, the ball-poppet is movable within a poppet guide that is allowed to float radially in order to allow the ball-poppet to be substantially self- centering with respect to the valve seat. In addition, cross-over leakage is preferably negated by closing an exhaust ball-poppet just prior to opening a supply balli-poppet. These principles and features are equally applicable to either or both of the primary or the multi-pressure selector fluid control valves. Ref. Fig. No. 1
Full Text The present invention relates to a selector fluid control valve.
BACKGROUND AND SUMMARY OF THE INVENTION
The invention relates generally to fluid control valves for operating a fluid-actuating device and more particularly to either selector or primary fluid control vsilvea employing one or more ball-poppets, Although the principles of the invention are applic able to both pneumatic and liquid fluid control valves, it is especially applicable to high-pressure pneumatic control valves, ' as well as to such pneumatic controls adopted for selective switching between, two. or .more different outlet pressures.
A variety of fluid control valves, especially those of the pneumatic nature, have been provided for numerous high-pressure applications, including those used in precedes for blow-molding plastic bottles or other such containers. Although.such control valves have generally runctioned sarisfectorily for the processes to which they have been applied, they have been found to be iubject to exceliive wear due to the high working fluid pressures, involved and thus.have had a relatively short life span. In addition, also in part due to the high pressures of the actuating fluids , such previously-provided fluid control valvss have baen subject to an unacceptable level of internal working fluid leakage, such as cross-over leakage that occurs when opening a supply portion of the valve and closing an exhaust portion of the valve in aider to admit working fluid to the fluid-actuating device. As a result, both of these factors have contributed to the high operajtion costs and high maintenance costs of the systems in which the previously-provided fluid control valves have been used.
In addition, many applications require the capability of selecting between two or more control valve outlet pressures, especially in pneumatic system, one example of such an
application is the above-mentioned processes for blow-molding plaatic bottles or other such vessels or containers. In these exemplary processes, it is often desirable or necessary to initially admit a relatively lower pressure to the mold in order to introduce the plastic (or other material) into the mold cavity or cavities and then to admit a relatively higher pressure to force or expand the material into the desired shape dictated by the shape of the mold
Therefore, the present invention seeks to provide an :mprovixi high-pressurre or multi-pressure fluid control valve that is significantly less subject to wear and that substantially negates internal working fluid leakage, thus contributing to the long life of he fluid control valve and reducing both system operating and .system, maintenance costs Furhermore the present inveotion also seeks to provide such a control valve capable of selectively delivering two or more different pressures to the process system
In accordance with the present invention, a primary control valve for operating a fluid-actuated device preferably has an inlet m communication with a source of pressurized working fluid, an outlet paisageway and port in fluid communication with the fluid-actuatad device, and a fluid supply pasaage providing fluid communication for ths working fluid from the inlet to the outlet. The control valve preferably includes a generally frusta-conical supply value seat in the fluid supply passage with the supply valve seat having a srtaller-diameter down/stream end and a larger-diaxneter upstream end. A generally spherical supply poppet or supply ball-poppet is selectively movable between respective supply closed and supply open positions, into and out of a substantially line-contact for sealing with the amalier-diametetr end of the supply valve seat. The spherical supply ball-poppet has a chord dimension at such .ine-contact with the smaller diameter downstream end of the valve seat that is smaller loan the larger-diameter upstream end of the supply valve seat. This arrangement can also be used in a pleasure selector fluid control valve according to the present invention, as described below.
Each side of the preferred frusto-conical supply valve seat, has a supply seat anflle relative to the centerline of the supply valve seat that is greater than an angle f ormed by the centerline of the supply valve seat and a line tangent to the supply ball-poppet at the above-mentioned substantially line-contact when the supply ball-poppet is in its closed position. The included angular relationship of the valve seat singles on both sides of the centerline is preferably approximately ninety degrees. Tills results in a annular space being formed between:, the supply valve seat and the spherical supply bail-poppet, which definss a restricted supply flow area upstream of the above-mentioned substantially line-contact as the supply ball-poppet initially moves to its open position and as high-velocity and high-pressure workng fluid initially flows downstream past the supply ball-poppet through the smaller-diameterand of the valve seat. This is greatly advantageous because any sonic flow erosion caused by tie initial flow of the high velocity and high-pressure working fluid through the annular ,-estricted supply flow area is thus shifted substantially immediately to an upstream surface of the supply valve seat that is adjacent to such annular restricted supply flow area Most significantly, su;h upstream surface of the supply valve seat is an area that is not sealingly contacted by ne supply oall-poppet Therefore, this immediate shifting of the sonic damage-susceptible area substantially minimizes sonic erosion of the nearly "knife-edge'! smaller-diameter downstream sand of the supply valve seat that is substantially line-contacted by the supply ball-poppet. In control valves according to the present invention that have berth supply vaiving and exhaust valving, a similar arrangement is preferably provided in the exhaust passage way m fluid comimuucat.on tor exhaust fluid between the load outlet passageway (and load outlet) and the exhaust outlet, as mentioned above, this arrangement is equally applicable to a pressure selector flu .a contra! valve, as described below.
In addition, the present invention preferably inudes a generally cylindrical cavity immediately upstream of the larger-diameter upstream enai of the supply and/or exhaust valve seats, with such cavity preferably being larger in diameter man the larger-diameter upstream end
of the respective valve seats. A cylindrical poppet guide or bat-poppet guide is located in this enlarged-diameter cavity of the fluid passageway, with the bali-poppet guide having a central guide bore extending axiaily therethrough. A number of cirourriferentally spaoed-apart axially-extending guide fins protrude radially inwardly into the guide oore, with the ball-poppet being received within the guide bore for axial movement within radially inward adges of the guide fins between its open and closed positions. The inner diameter of the abovij-mentioned oavity is preferably slightly greater than the outer diameter of the bail-poppet guide in order to allow the ball-poppet guide and the ball-poppet to float radially somewhat within the cavity, This allows the generally spherical ball-poppet to be substantially self-centering fer scaling line- contact with the smaller-diameter end of the respective supply or exhaust valve sea, Such circumferentially spaced guide flns allow high pressure working fluid to flow thcrebetween and the ball-poppet guide substantially minimizes wear on the ball-poppet and/or the valve seat that would result if it were to be allowed to rattle or otherwise move radially ir. The high-velocity fluid flow. Such a ball-poppet guide can also b« used in a selector fluid control vaive, as described below,
The present invention substantially also negates cross-over leakage in high-pressure fluid control valves having both supply and exhaust valvmg by snergizing the exhaust ball-poppet actuator, thus closing the exhaust aide of the control valve, just prior to energizing the supply ball-poppet actuator, which then opens the supply side and initiates supply flow to the load passageway and port:.
The above-mentioned ball-poppets (for either primary or selector fluid control valves) are preferably composed, of n metallic material, such as a stainless steel, for example, and the above-mentioned ball-poppet guides are preferably composed of a synthetic material, such as nylon, for example. Those skilled in the art will readily recognize that other metallic, synthetic, or non-synthetic materials can also be employed for the ball poppots and/or the ball-poppet guides, depending upon the particular working fluid (pneumatic or liquid) being employed, as
well as the particular working fluid pressures involved, aa well as depending upon the particular application in which the fluid control valve of the present invention is employed.
The present invention also provides a pressure selector fluid control valve for selectively supplying at least two different working fluid pressures to a fluid-actunted device, either directly or by way of a primary fluid control valve, such as that discussed above. An exemplary selector fluid control valve according to the present invention preferably has a high-pressure inlet in fluid communication with a source of working fluid at a relatively high pressure, a low-pressure inlet in fluid communication with a source of working fluid at a relatively lew pressuie. and a load fluid outlet passageway interconnected in fluid communication wit a the fluid-actuated device or primary fluid control valve inlet. Such a selector fluic; control valve further includei a normally closed high-prassure valve mechanism in fluid cammurication between the high-pressure inlet and the load fluid outlet passageway to selectively allow high-pressure fluid flow from the high-pressure inlet to the load fluid outlet passageway, as well aa a normally open low-pressure valve mechanism in fluid communication between, the low -prassure inlet and the load fluid outlet passageway to selectively allow low-pressure fluid flow from, the low-pressure inlet 10 the load fluid outlet passageway, A pilot actuator is provided aid is selectively operable to force the normally closed high-pressure valve mechanism into an open position and allow said high-pressure fluid flow from the high-pressure inlet to the load find outlet passageway. This high-pressure fluid being admitted into the load fluid outlet passageway forow the normally open low-pressure valve mechanism into a closed position to prevent fluid flow between the low-pressure inlet and the load fluid outlet passageway Thus trie selective actuation or energization of the pilot actuator, either the high-pressure or low-presstue working fluid (such as a pneumatic working fluid, for example) can be admitted to the inlet of a fluid-actuated device or the inlet of a primary fluid control valve, such as that described abova or of' virtually any type.
At least one or preferably both of the above-discussed high-pressure and low-pressure valve machaniams can include a generally frustc-conieai valve seat located m a valve fluid passageway in fluid communication with the load fluid outlet passageway, with tha valve seat having a smaller-diameter downstream end and a larger-diairieter upstream end. A generally spherical ball-poppet is selectively movable between respective closed aad open positions into and out of substantially ball-poppet line-contact for sealing win said smaller-diameter end of the supply valve seat, Thegenerally spher.cai ball-poppet prefera sly has a chord dimension at said line-contact with the smaller-diameter downstream end of the valve seal that is smaller than the larger-diameter upstream end of the valve seat The generally frusto-corucal valve seat preferably has a seat angle relative to the centerlme of the supply va.ve seat that in greater than an angle formed by the centerlirie of the valve seat and a line rangent to the spherical ball-poppet at the ball-poppet line-contact when the ball-poppet is m said cios sd position, with such seat angle preferably being approximately forty-five degrees such that the overall seat angle between diametrically opposite portions of the valve seat IB approximately ninety degreed An annular space formed between the valve seat and the spherical bail-poppet tius defines a restricted flow area upstream of tlie ball-poppet line-contact between the spherical ball -poppet and the smaller-diameter downstream end of the valve seat as the spherical ball-poppet initially moves out of said line-contact to its open position ana as the working fluid imt ally- flows downstream paet the ball-poppet through the smaller-diameter end of said valve seat. By such an arrangement, any sonic flow erosion caused by the initial working fluao flow past the opening ball-poppet is shifted substantially immediately to an upstream area of the valve seat that is adjacent the restricted flow area and that is not sealmgly contacted ny the spheru.a: bali-poppet. This substantially minimizes sonic damage to the smaller-diameter downstream end of said valve seat against which the ball-poppet is sealingly engaged when m its closed position- This greatly increases the life of the control valve oy minimizing the wear on the seairing portion of the valve seat,
One or both of the fluid valve passageways can include a generally cylindrical cavity immediately upstream of the larger-diameter upstream, end of the valve seat, the cavity being larger in diameter than the larger-diameter upstream end. The valve mechanism preferably includes a generally cylindrical ball-poppet guide located in the cavity of said fluid passageway, with the bail-poppet guide having a central guide bore extending axially therethrough. The ball-poppet guide preferably has a number of oircumferentiaily spaced-apart axially-extanding guide fins protruding radially inwardly into the guide bore, 'with the ball-pep pet being received within . the guide bore for axial movement within radially inward edges of the gulde fins between its open and closed positions. The inner diameter of the cavity is greater than the outer diameter of • the ball-poppet guide in order to allow the ball-poppet guide no float radially within the cavity and to allow the sphorical ball-poppet to be substantially self-centering ibr sealing line-contact with the smaller-diameter end of said frusto-conical valve seat.
In any of the primary or pressure selector fluid control valves according to the present invention, the frusto-conical valve seat can alternatively be located in 2, replaceable valve seat disc that is of a harder material than 'that of the valve body,
Additional objects, advantages, and features of the present invention will become apparent from the following description and the appended claims, taken in conjunction with the accompanying drawings.

Accordingly the present invention relates to a selector fluid control valve (210, 410) for selectively supplying two different working fluid pressures to a fluid-actuated device, said selector fluid control valve (210, 410) having a high-pressure inlet (220, 420} in fluid communication with a source of working fluid at a relatively high pressure a low-pressure inlet (221, 421) in fluid communication with a source of working fluid at a relatively low pressure, and a load fluid outlet passageway (228, 428) interconnected in fluid communication with the fluid-actuated device, said selector fluid control valve (210, 410) further having a normally dosed high-pressure valve mechanism in fluid communication between said high-pressure inlet (220, 420) and said load fluid outlet passageway (228, 428) to selectively allow high-pressure fluid flow from said high pressure inlet (220, 420) to said load fluid outlet passageway (228, 428), and a normally open low-pressure valve mechanism in fluid communication between said low pressure inlet (221, 421) and said load fluid outlet passageway (228. 428) iu selectively allow low-pressure fluid flow from said low-pressure inlet (221, 421) to said load fluid outlet passageway (228, 428), said selector fluid control valve (210, 410) further having a pilot actuator (280, 480) selectively operable to force said normally closed high-pressure valve mechanism into an open position and allow said high-pressure fluid flow from said high-pressure inlet (220, 420) to said load fluid outlet passageway (228, 428) said high-pressure fluid in said load fluid outlet passageway (228, 428) forcing said normally open low- pressure valve mechanism into a closed position to prevent reverse fluid flow between said high pressure inlet (220, 420) and said low-pressure inlet (221, 421} , characterized in that one of said high pressure and low-pressure valve mechanisms comprises fmsto-conical valve seat (36, 46, 236, 246, 336, 436) located in a vaive fluid passageway in fluid communication with said load fluid outlet passageway (228, 428), said valve seat (36, 46, 236, 246, 336, 436) having a smaller- diameter end (38, 48, 238, 248, 438) and a larger-diameter end (40, 50. 24O, 250), and a spherical ball-poppet (42, 52, 242, 252, 342, 442, 452} being selectively movable between said respective closed and open positions into and out of ball-poppet line-contact (44, 54, 344) for scaling with said smaller-diameter end (38, 48, 238, 248, 438) of said supply valve seat (36r 46, 236, 246, 336,
436), said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) having a chord dimension at said line contact (44, 54, 344) with said smaller-diameter end (38, 48, 238, 248, 438) of said, valve scar (36, 46, 236, 246, 336, 436) that is smaller than said larger-diameter end (40, 50, 240, 250) of said valve seat (36, 46. 236, 246, 336. 436), said trusto-conical valve scat (36, 46, 236, 246, 336, 436) having a scat angle (37, 47) relative to the centerline (57, 67) of said valve seat (36, 46, 236, 246, 336, 436) that is greater than an angle (59, 69) formed by the centerline (57. 67) of said valve seat (36, 46, 236, 246, 336, 436) and a line (56, 66} tangent to said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) at said ball-poppet line-contact (44, 54, 344) when said ball-poppet (42, 52, 242, 252, 342, 442, 452) is in said closed position, an annular space (43, 53) formed between said valve seat (36, 46, 236, 246, 336, 436) and said spherical ball-poppet (42, 52, 242, 252, 342, 442. 452) defining a restricted flow area adjacent said ball-poppet line-contact (44, 54, 344) between said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) and said smaller diameter end (38, 48, 238, 248, 438) of said valve seat (36, 46, 236, 246, 336, 436) as said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) initially moves out of said line-contact (44, 54, 344) to its open position and as said working fluid initially flows past said ball-poppet (42, 52, 242, 252, 342, 442, 452), any sonic flow erosion caused by said initial working fluid flow thereby being shifted immediately to an upstream flow area that is adjacent said ball-poppet line-contact (44, 54, 344) arid that is not sealingly contacted by said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) thus minimizing sonic damage to said smaller- diametei end (38, 48, 238, 248, 438) of said valve seat (36, 46, 236, 246, 336, 436)
BRIEF DESCRIPTION OF THE ACCOMPANYING DRAWINGS
Figure 1 is a cross-sectional illustration of an exemplary fluid control valve according to the present invention.
Figure 2 is an end view of the fluid control valve of Figure i ,
Figure 3 is a top view of the fluid control valve of Figures 1 and 2, with the top cover or cap removed.
Figure 4 is atop view oi a bait-poppet guide foi use with either or both of a supply ball-poppet and art exhaust ball-poppet of the control valve of Figure 1
Figure 5 is a side view of the poppet guide of Figure
Figure 6 is an enlarged detail view oi ttie supply vaiving portion of the control valve of Figure 1, with the supply ball-poppet shown in its closed position
Figure 7 is an enlarged detailed view similar to that of Figure a, but illustrating the supply ball-poppet in its initially opening condition
Figure 8 is an enlarged detail view of the ewiaust vaving portion of the control valve of Figure 1, with the exhaust ball-poppet shown in its closed position
Figure 9 is an enlarged detail view similar to that of I igure 8 but illustrating the exhaust ball-poppet in its initially opening condition
Figure 10 is a cross-aectionai illustration of an exemplary iual-pressure selector fluid control valve according to the present invention
Figure l0a is a cross-sectional view taken generally along jne l0a- 10a of Figure 10
Figure 11 is a top View of the exemplary dual-pressure selector fluid control valve of Figure 10, operatively interconnected with a primary fluid control alve. luch as is illustrated in Figures 1 through 9, both of which baing mounted on a fluid man. for
Figure 12 is a front view of the fluid control valve arrangement of Figure 11
Figure 13 is an end view of the fluid control valve arrangement of Figures 11 and 12
Figure 14 is a cross-seotional illustration of an exeiaplary pressure selector fluid control valve similar to that of Figure 10, but showing an alternate tri-pressure version of the selector fluid control valve
Figure 15 is an enlarged detailed view of an alternate version of the ball-poppet portion of a control valve according to the invention, having a repiaceabje v aive seat disc and which is applicable to any of the fluid control valves of Figures 1 through. 14
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS
Figures 1 through 15 illustrate exemplary high-pressure and multi pressure primary and selector pneumatic control valve in accordance with the present invention. Although the drawings depict such exemplary pneumatic fluid control valves for purposes of illustration, one skilled in the art will readily recognize that the principles of the present invention are equally applicable to other types of primary or selector fluid control valves, as well as to fluid control valves for either pneumatic or liquid working fluids.
In Figure 1, an exemplary primary fluid control valve 10 includes a body 12, apilot cap 14, both of which can be secured to a manifold 16 by way of a nun her of bolts 18, as well as being capable of alternate interconnection by way of fluid piping without the use of the manifold 16 if threaded ports are alternately provided
The exemplary primary control valve 10 includes an inlet pc rt 20, an outlet or load port 22, and an exhaust port 24 A working fluid supply passageway 28 provides working fluid communication from the inlet port 20 to the outlet pan 22, which if connected, such as by way of the manifold 16, to a fluid-actuated device. Similarly, in exhaust passageway 30 provides exhaust fluid communication between the load port 22 and. the exhaust outlet 24.
In the exemplary primary control valve 10, the supply and exhaust passageways 28 and 30 respectively include a frusto-conical supply valve seat 3 5 and a frusto-oonical exhaust valve seat 46, The supply valve seat 36 includes a smaller-diameter end :i8 and a largur-diameter end 40, Similarly the exhaust valve seat 46 includes a smaller-diameter end 48 and a larger-diameter end 50, A generally spherical supply ball-poppet 42 and a similar generally spherical exhaust ball-poppet 52 are provided for opening and closing movement with respect to their respective fruato-conical supply and exhaust valve ssati 36 and 46,
The supply ball-poppet 42 is preferably movably actuated by way of a supply pilot actuator 80, which receives pilot air from a pilot air passageway 97, which is in rum connected
in fluid communication with a pilot air inlet 96, Whan the supply piloi acmator 80 in energized, it transmits the force of the pilot air on the supply piston 81, by way o a supply push rod 82, to urge the supply ball-poppet 42 away from the iupply valve jseat 36, thus opening the supply valving portion of the control valve 10, When the supply pilot actuator 80 is deec.ergized, the ball-poppet 42 is returned to its closed position under the influence of :he inlet fluid pressure and a return spring 58.
Similarly, the exhaust bsJi-poppet 52 is urged mto its closed position with respect to the exhaust valve seat 46 by way of the energization of an exhaust pilot actuator 90, which acts to exert the force of pilot air on an exhaust piston 91, by way of an exhaust push rod 92, to the exhaust ball-poppet 52, Upon cieenergization of the exhaust pilot actuator 90, the exhaust ball-poppet 52 ifi urged back to its open position under the influence of hgh-pressure working fluid in the exhaust passageway 30,
One skilled in the control valve art will readily recognize tt4t actuators other than the exemplary electro-pneumatic supply pilot actuator 80 and electro-pneumatic exhaust pilot actuator 90, can altemativaly be employed. Such actuating devices could include electromechanical solenoids, either local or remote, mechanical motion trenaniitting devices, or a wide variety of other actuating devices well-known to those skilled in the art,
Referring primarily to Figures 6 and 7, the exemplary high-pressure fluid control valve 10 depicted in the drawings also preferably includes a generally cylindrical supply cavity 60 immediately upstream of the larger-diameter upstream end 40 of the supply vaive seat 36, As illustrated in Figures 4 through 6, a generally cylindrical supply poppet guide 62 is provided upstream within the preferred diametrically-enlarged cylindrical supply cavity 60, The supply poppet guide 62 includes a generally cylindrical central supply gude bore 64 extending axially therethrough, with a number of circumferential!}- spacea-apart and axially-attending supply guide fins 66 protruding radially inwardly into the supply guide be re 64, The supply ball-poppet
42 is received within the supply guide bore 64 for axial movement within. the radially inward edges of the supply guide fins 66 between its opm and closed potations with respect to the supply valve soat 36, As is perhaps best illustrated in Figures 6 and 7, the inncx diameter of the supply cavity 60 is slightly greater than, the outer diameter of the supply baa-poppet guide 62, thus allowing the poppet guide 62 and the ball-poppet 42 to float radially wi iur; the supply cavity 60, which in turn allows the generally spherical supply ball-poppet 42 to ba sclf-centerinfj for sealing substantially line-contact 44 with the smailer-diamater end 38 of the supply valve .seat 36,
In addition, the supply guidi fins 66 preferably exter.d axial iy downstream to form a supply guide tin extension portion 63 on one end of the supply poppat guide 62. A resilient nng 61, such as an O-ring, surround the extension portion 63 in order to -esiiiently urge the poppet guide 62 toward the opposite, upstream end of the supply cavity 60, which is due to the resilient nng 61 being compressed between 'the floor of the supply cavity 60 ard the remainder of the supply ball-poppet guide 62
It should be noted that the above arrangement, as depicted in Figures 4 through 1, is substantially typical with respect to the frusto-conical exhaust valve seat 46, with its smaller-dianaeter upstream end 48 and its iargor-diamcter downstream ond 50 for engagement in substantial line-contact of the smaller-diameter end 48 by the generally spherical axhaust poppet 52, all of which are shown la Figure 1. Similarly, the supply poppet guide 62 depicted in Figures 4 and 5 is substantially typical for the exhaust poppet guide 72, v/hich is received within the diametrically-enlarged generally cylindrical exhaust cavity 70 and has a similar central exhaust guide bore 74 and similar exhaust guide fins 76, and which can also ba seen in Figures 1, 8 and 9.
Referring in particular to Figures 6 and 7, which depict as enlarged detail view of the supply valving portion of the exemplary- control valve 10. the ball-poppet 42 is shown in its; closed position in Figure 6, In this position, the ball-poppet 4," is sealmgly engaged in

substantial line-contact 44 with the edge of the smaller-diameter and 3,'J of the supply valve seat 36, Similarly, the bail-poppet 42 is shown partially opened and fius moved out of such substantial line-contact 44 in Figure 7 The fruaro-conical supply valve /seat 36 preferably has a valve seat ajigle 37 (with respect to the centerline 57 of the viiive seat 36) that is slightly larger than the tangent angle 59 of the tangent line 56 to the bal -poppet 42 (with respect to the centerline 57.) whoa the ball-poppet 42 is in the substantial hne-eont'icf -44 shown in Figure 6,
This arrangement results in an annular space 43 creating a resoicwid supply flow area juat upstream of the supply line-contact 44 and the smalier-diametin" end 38 as the supply ball-poppet 42 initially moves out of such line-contact 44 ro us openposiaon she wn in Figure as working fluid initially flows downstream past the ball-poppet 42 throiigh the smaller-diameter end 35 of the supply valve seat 36. This results m any sonic flow erosion dar.iags caused by such initial flow of high-pressure working fluid to bs shifted substantially immediately to an upstream area 45 of the supply valve seat 36, This is highly advantageous 11 that it shifts such wsar or damage caused by auch some flow erosion to an area of the suppb vaive sea', 36 that is adjacent the annular apace 43 and that is never tn sealing contact with thss ball-poppet 42 This substantially minimizes sonic damage to the smaller-diameter downstream sealing and 38 of the supply valve seat 36 which is the only valve seat area that is ever m substantial one- contact 44 with the ball-poppet 42. As a result, the damage to and wear of the accuai sealing surface of the vaive seat 36 on the ball-poppet 42 is very substantially minimized and the functional life of the exemplary control valve 10 is correspondingly greatly extended This m turn very significantly reduces the downtime and the maintenance coats for a system employing a control valve 10 according to the present invention
As will be readily recognized by one skilled in the art, that the above-deacribed function of the ball-poppet 42 with respect to the supply valve sea: 36 as the m. in Figure 6 and Figure
IE similar to that of the function and relationship of the exhau;it ball-poppet 52 with respect to the exhaust valve seat 46 with its smaller-diameter end 48 and its iarg'.T-diameter aid 50.
Referring primarily to Figiures 8 and 9, the exemplary high-pressure fluid control valve 10 depleted in the drawings also preferably includes a generally cylindrical exhauut cavity 70 immediately downstream of (he larger-diameter downstream end 50 of the exhaust vulve seat 46, A generally cylindrical exhaust poppet guide 72 (similar to that of the supply poppet guide 62 of Figures 5 and 6) is provided downstream within the preferred diametrically-enlarged cylindrical exhaust cavity 70, The exhaust poppet guide 72 includes a generally cylindrical central exhaust guide bore 74 extending axially therethrough, wth a nanber of ciratrnferentially spaced-apart and axially-extending exhaust guide fiixs 76 protruding racially inwardly into the exhaust guide bore 74. The exhaust ball-poppet 52 is received within the exhaust guide bore 74 for axial movement within the radially inward edges of the axhaus, guide tins 76 between its open and closed positions with, respect to the exhaust valve seat 46. The inner diameter of the exhaust cavity 70 is slightly greater than the outer diameter of the ejjaaust bali-pojjpet guide 72, thus allowing the poppet guid« 72 and the exhaust ball-poppet 52 to float radutliy within the exhaust cavity 70, which in turn, allows the generally spherical exhaust oali-poppet 52 to be self-centenng for sealing substantially line-contact 54 with the smaller-diameter end 48 of the exhaust valve seat 46.
The exhaust guide fins 76 preferably extend axially upstre in to form, an exhaust guide fin extension portion 73 on the exhauet poppet guide 72, A resident ring 71, such as an O-ring, surrounds the extension portion 73 in order 10 urge the poppet guida 72 toward the opposite., downstream end of the exhaust cavity 70, which is due to the resilent nng 71 being compressed between the floor of the exhaust caviry 70 and the remainder of the exhaust ball-poppet guide 72,
Referring in particular to Figures 6 and 9, which depict an enlarged detail view of the exhaust valving portion of the exemplary control valve 10, the exhaust ball-poppet 52 is shown In its closed position in Figure B. In this position, the ball-poppet 52 is sealingly engaged in substantial line-contact 54 with the edge of the smaller-diameter end 41 of" the exhaust valve seat 46. Similarly, the ball-poppet 52 is shown partially opened and rhue moved out of such substantial line-contact 54 in Figure 9 The frusto-comcal exhaust value seat 46 pi eferably has an exhauat valve seat angle 47 (with respect to the exhaust cen .erline 11 of the valve seat 46) that is slightly larger than the exhauat tangent angle 69 of the exhaust tangent tine 65 to the exhaust ball-poppet 52 (with respect to the centeriine 67) when the tall-poppet 52 is in the substantial line-contact 54 shown in Figure S
This arrangement results in an annular space 53 creating a restricted exhaust flow area just downstream of the exhaust line-contact 54 and the smaller-diainetur end 48 as the exhaust ball-poppet 52 initially moves out of such line-contact 54 to its untially opening position shown m Figure 9 as exhauat fluid initially flows downstream past the sall-poppet 52 through the smaller-diameter and 48 of the exhaust vah e jeat 46 Thus; in any sonic flow erosion damage caused by such initial flow of high-pressure exhaust fluid to be shifted substantially immediately to an upstream flow area adjacent the exhaust valve seat 46 This if highly advantageous in that it shifts such wear or damage caused by such sonic flow erosion to an area that is never in scaling contact with the ball-poppet 52 This substantially minimizes sonic: damage to the smaller-diameter upstream sealing end 48 of the exhaust valve seat 46 which :s the only valve seat area that is ever in substantial line-contact 54 with the oall-poppet 32. as. remit, the damage to and wear of the actual sealing surface of the valve seat 46 on tte ball-p oppet 52 is very substantially minimized and the functional life of the exemplary control valve 10 s correspondingly greatly extended. This m turn very significantly reduces me downtime and the maintenance costs for a system employing a control valve 10 according to the present invention
Referring primarily to Figure 1, the cross-over leakage of the exemplary fluid control valve 10 depicted in the drawings is substantially minimized by energizing the exhaust pilot actuator 90 to close the exhaust ball-poppet 52 just slightly prior to energizing the supply pilot actuator 80 to open the ball-poppet 42 when high-pressure working fluid is to be admitted to the outlet or load port 22 in order to actuate a fluid-actuated device. Because of the equipment and energy necessary to elevate fee -working fluid to such a high-pressure state, this greatly reduces the operating costs that would otherwise result from excessive waste cr exhaust of high-pressure working fluid. Such high-pressure working fluid, which can be either paeumatic or hydraulic, but which is preferably pneumatic, is often in the range of 300 psig to 900 piig, arid is typically approximately 600 psig in the above-mentioned blow-molding procsssos.
Finally, either or both of'the ball-poppets 42 and $2 arc; preferably composed of a metallic material, such as stainless Steel or other metallic or non-metallic mate dais deemed advantageous by one skilled in the art for a given application. Similarly, cither o • both of the nupply poppet guide 62 and the exhaust poppet guide 72 are preferably composed of a synthetic material, such as nylon, but can also be composed of a metallic material, such a staniass steel, or other suitable materials known to those skilled in the art,
Figures 10 through 15 illustrate various versions of 2, selector fluid control valve that can be us,ed either alone or in conjunction (on the supply side) with the primary fluid control valve discussed above in connection with Figures 1 through 9, Because mfoiy of the components of the valves illustrated in Figures 10 through 15 are either identical on substantially similar, at least in function, with those of the valves depicted in Figures 1 through , such components in Figurers 10 through 15 are indicated by reference numerals that are the samn as those ui Figures I through 9, but which have two hundred, three hundred, or four hundred prefixes
In Figures 10 through 13, an exemplary selector fluid control valve 210 includes abody 212, apilot cap 214, both of which can be secured to a manifold. 216 (as shown in Figures 11
through 13) in a manner similar to that depicted above in eo.mectioa with Figures 1 through 9, Alternately, however, instead of a manifold 2! 6, interconnection o the various ports could be accomplished by way of fluid piping without the use of the niarufolc 216 by prov: ding threaded pong in the base of the valve body 12
The exemplary selector fluid control valve 210 incudes a relat.vely high-pressure inlet port 220 and a relatively lower-pressure inlet port 221, which are; ,1 flaid communication with separate sources of working fluid at relatively higher pressures or lower pressures, respectively. Such relatively higher pressures will he referred to herein as 'high-pressure, and. such relatively lower pressures will similarly be referred :o as low-press xre
A load fluid outlet passageway 228 extends through the body 212 of the selector fluid control valve 210 and is in fluid communication with an ou;let loac port 222. Th« selector fluid control valve 210 can be used either alone, or in combmarion with .1 primary fluid control valve, such as the primary fluid control valve :0 of Figures . through 9 In such an application, the selector fluid control valve 210 can. have its load outlet pun 222 interconnected in fluid communication with the inlet port 20 of the primary fluid control valve 10, either by fluid piping or by way of the manifold 216
The selector fluid control valve 21C also includes a normai y closed high-pressure valve mechanism in fluid commurucation oetweeti the high pressure input port 22C and the ioad fluid outlet passageway 228, Similarly, a normally open iow-preasure va,ve mechanism is in fluid communication between the low-pressure inlet port 221 and the oad fluid ou'let passageway 228. In the exemplary selector fluid control valve 210, the high-pressure valve mechanism includes a fhisto-conical valve seat 236. which in turn includes a ;mailer-dlamtiter end 238 and a larger-diameter end 240, A ball-poppet 242, which is pieferably generally spherical m ahape and oonfiauration, engages the valve seat 236 in a substantially ine-contact engagement, in a manner explained in more detail in connection with the vaive sea; of and the ball-poppet 42 of

Figures 1 through 9. Similarly, the low-pressure valve mechanism includes a valve seat 246 having a smaller-diameter end 248 and a larger-diameter end 250, with the low-pressure ball-poppet 252 engaging the small-diameter end 248 m the same rypc or lina-contact us is discussed above,
The high-pressure ball-poppet 242 is received within a tugb-prussure bat -poppet guide 262, which ii similar to the ball-poppet guide 62 of Figures ! through 9, In a stmilar manner, the low-pressure ball-poppet 252 is received within a low-pressure high-poppet guide 272, In terms of their radially-floating and ball-poppet centering capabilities, the guides 262 and 272 are substantially identical to the guides 62 and 72 of Figures 1 through 9, The only difference between the guidei 262 and 272 and the above-discussed guides 62 and 72 is that the fins 266 and 276 do not necessarily extend axially beyond the end of their re ipocnve guides 262 and 272 In such an arrangement, instead of the O-nngs 61 and 71 of Figures 1 through 9 resilient wavy waihers or spring wave washers 261 and 271 are provided to retilisntly bias the respective guides 262 and 272 toward their respective proper positions within the respect ve guide bores 264 and 274, In substantially all other respects, however, the bal -pcppet guides 262 and 272 perform in a substantially identical manner as the corresponding ball-poppet guides 62 and 72 discussed above
In the preferred selector fluid control valve 210, the high-pranura ball-poppet 242 is biased toward its normally closed position by a return spring 258 icting on the bail-poppet 242 by way of a ball-poppet perch 275, A pilot actuator 280 Is provide i in connection with the high-pressure ball-poppet 242 and is selectively actuable :o force the ball-poppet 242 off of its respective valve geat 236 and into its open position, with the pile: actuator 280 acting through the high-presiure actuating piston assembly 281 and the push roc 282
In the low-pressure valve mechanism, the ball-poppet 252 is m a normally-open position under the influence of the low-pressure working fluid from the low-pressure inlet 221 actingon the ball-poppet 252 and against the biaaing force of a low-force retaining spring 251. The
low-pressure ball-poppet 252 is held in place by a retainer plug 249 raving a generally U-shaped
opening 278 extending therethrough, as is illustrated in Figure l0a, and the opening travel of the
low-presure ball-poppet 252 it limited by its contact with a stop rod or pin 277 fixedly
interconnected with the retainer plug 249 and extending into the retainer plug paasageway 278.
In operation, the selector fluid control valve 210 can be used to selectively supply one
of two different pressures of working fluid (preferably a pneumatic working fluid) to either a
fluid-actuated device or to the inlet of a primary control valve (such as the primaiy fluid control
valve 10 discussed above) by way of the outlet load port 222 of the selector fluid control valve
210. Initially, a source of relatively low-pressure working fluid is supplied to the low-pressure
inlet port 221 and passes by the normally-open ball-poppet 252 to the load fluid outlet
passageway 228 and the outlet load port 222. Such relatively low-jireesure working fluid exerts
sufficient force on the low-pressure ball-poppet 252 to maintain it in jti open position against the
biaaing force of the low-pressure retaining spring 251 as long as fluid is flowing in the circuit.
Thus, in this condition, as is illustrated in Figure 10, relatively high-pregiure working fluid
supplied to the high-pressure inlet port 220 ia isolated from the relatively low-pressure working
fluid in the load fluid outlet passageway 228 by the normally closed high-pressure ball-poppet
242, which is forced against its respective valve seat 236 under the influence of the return spring
258. Thus, in this condition, such relatively low-pressure working fluid is supplied to the outlet
load port 222.
However, when it it desired to admit relatively high-pressure working fluid to the load fluid outlet passageway 228 and to the outlet load port 222, the pilot actuator 230 is selectively energized. It should be noted that the pilot actuator 220 can be pneumatically operated, electrically operated, or mechanically operated, for example.
The energization of the pilot operator 280 causes the piston assembly 283 and the push rod 282 to force the high-pressure ball-poppet 242 to its open position against tho biasing force of the return spring 258 and the high-pressure fluid in the inlet 220, This opening of the high-pressure ball-poppet 242 allows relatively high-pressure working fluid from the high-pressure inlet port 220 to pasf into the load fluid outlet passageway 228. The high-pressure working fluid now admitted into the load fluid outlet paseageway 228 acts (in cor junction with the low-force retaining spring 251) to urge the normally open low-pressure ball-poppet 252 to its closed position in sealing engagement with the valve seat 246, Tims, in this condition, the relatively low-pressure working fluid from the low-pressure inlet port 221 is isolated from the relatively high-pressure working fluid in the load fluid outlet passageway 228, the retainer plug passageway 278, and the outlet load port 222. Ae mentioned above, this allows for selective supply of either the relatively low-pressure working fluid or the relatively high-pressure working fluid from fho outlet load port 222 to a fluid actuated device or to the inlet 20 of a primary valve auch as that of the primary control valve 10 Illustrated in Figures through 9 This latter arrangement is illustrated in Figures 11 through 13 where this selector fluid control valve 210 and the primary control valve 10 are mounted together on a marufoid 116 which can alternately be replaced by separate fluid piping without the use of the manifold 216 ,f alternate threaded ports are provided.
In Figure 14, an alternate embodiment of a selector fluid control valve according to the present invention ii depicted for purposes of illustrating that the present invention is equally applicable to such control valves adapted for supplying more than two different working fluid pressures to a fluid-actuated device either directly or through a pnnary fluid control valve, such as the primary fluid control valve 10 discussed above ana shown m Figures 1 through 9, The selector fluid control valve 410 in Figure 14 has numerous components that are either identical or functionally substantially similar to those of the fluid selector control valve 2:10 in Figure 10.
In Figure 14. however, such corresponding components are indioafed by reference numerals having four-hundred prefixes and a or b suffixes in the case of components that are identical with each other.
The body 412 of the selector fluid control valve 410 includes two of the above-discussed high-pressure inlets 420a and 420b, with two of the above-deacribod pilot actuarora 480a and 480b, each of which are separately and selectively operable to urge tieix respective ball-poppets 442a and 442b into their respective open positions, In virtually all other respects, however, the selector fluid control valve 410 operates in substantially the some meaner as the above-described selector fluid control valve 210,
The operational difference between the selector fluid control veilve 410 and the selector fluid control valve 210 is that the pilot actuators 480a and 480b can be separately and selectively actuated or energized, or de-actuated or de-energized, in order to allow for the selective supply of three different pressures or working fluid to the fluid-actuated device, by way of the load outlet port 422, either directly or by way of the above-mentioned prinuiry fluid control valve. It should be noted that Figure 14 illustrates merely an exemplary muli-pressure application of the present invention, and one skilled in the art will now readily reuogaize that any number of different pressures can be accommodated by the selector fluid control valve of the present invention.
In Figure 15, still another alternate arrangement of the present invention is depicted, in which the resilient spring wave washer 361 is moved to an opposite position with respect to the ball-poppet guide then that depicted in Figure 10, In this arrangement, a replaceable valve seat disc 388, which includes the valve seat 336 therein, is trapped between the ball-poppet guide 362 and the downstream end of the guide bore 364. The valva seat disc 388 includes a chamfered edge 386 that is sealingly engaged by an 0-ring 384 and is preferably composed of a harder material than that of the valve body- Such an arrangement allows for convenient replacement
of a worn valve seat 336 by merely replacing the valve seat disc 388, without the necessity of discarding or re-machining the valve seat 236 of ihe body 2l'l m Figure 10, Thus, one selector fluid control valve can be partially disassembled and repaired by such replaoement of the valve seat disc 388 while another selector fluid control valve is us service, Such repaired selector fluid control valve can then be maintained in reserve for unmedittte replaement of a worn selector fluid control valve that is currently in service. It should be noted thai a similar replaceable valve seat disc can also alternatively be used m conjunction with any o" the valve mechanisms or arrangements shown in Figures 1 through 15
Finally, the preferred pneumatic high-pressure working fluid or fluid can be at virtually any pressure} above that of the low-pressure working fluid, such as, lor example, pressures in the range of 300 psig to 900 psig, with one application requiring a high-pressure working fluid at approximately 600 psig. Similarly, the low-pressure working flud can be ai virtually any pressure lower than that of the high-pressure working fluid, such as., for example, pressures in the range of 10 psig to 300 psig, with at least one application requiring such low-pressure working fluid at a pressure of approximately 100 psig. Furuaermc're, as mentioned above, the primary fluid control valves and the selector contra, valves of the present invention have wido-ranging applicability in various liquid or pneumatic fluid centre! or actuation systems, One example of such an application is a pneumatic system for blow molding, of plastic bottles or other containers, which requires a first relatively lower pressure to uigt this plastic material into the mold cavity, followed by a relatively lughar pressure working fluid to complete the blow molding process by forcing the plastic material against the; mtenwl contours of the mold, One skilled in the art will readily recognize, however, that this is mersly one example of the many applications of the present invention
The foregoing discussion discloses and describes merely exemplary embodiments of the present invention for purposes of illustration only. One sldlled ir the art wul mdily recognize
eueh dincusalon, and fom the accompanying drawing and claims, that various changes, modifications, and variations can be made therein without departing 6 cm the spirit and scope of the invention as defined in the following claims.





WE CLAIM:
1. A selector fluid control valve (210, 410) for selectively supplying two different working fluid pressures to a fluid-actuated device, said selector fluid control valve (210, 410) having a high-pressure inlet (220, 420) in fluid communication with a source of working fluid at a relatively high pressure, a low-pressure inlet (221, 421) in fluid communication with a source of working fluid at a relatively low pressure, and a load fluid outlet passageway (228, 428) interconnected in fluid communication with the fluid-actuated device, said selector fluid control valve (210, 410) having a normally closed high-pressure valve means in fluid communication between said high-pressure inlet (220, 420) and said load fluid outlet passageway (228, 428) to selectively allow high-pressure fluid flow from said high- pressure inlet (220, 420) to said load fluid outlet passageway (228, 428), and a normally open low-pressure valve means in fluid communication between said low-pressure inlet (221, 421) and said load fluid outlet passageway (228, 428) to selectively allow low-pressure fluid flow from said low-pressure inlet (221, 421) to said load fluid outlet passageway (228, 428), said selector fluid control valve (210, 410) having a pilot actuator (280, 480) selectively operable to force said normally closed high-pressure valve means into an open position and allow said high-pressure fluid flow from said high-pressure inlet (220, 420) to said load fluid outlet passageway (228, 428), said high-pressure fluid in said load fluid outlet passageway (228, 428) forcing said normally open low- pressure valve means into a closed position to prevent reverse fluid flow between said high-pressure inlet (220, 420) and said low-pressure inlet (221, 421) , characterized in that one of said high- pressure and low-pressure valve means comprises frusto-conical valve seat (36, 46, 236, 246, 336, 436) located in a valve fluid passageway in fluid communication with said load fluid outlet passageway (228, 428), said valve seat (36, 46, 236, 246, 336, 436) having a smaller- diameter end (38, 48, 238, 248, 438) and a larger-diameter end (40, 50, 240, 250), and a spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) being selectively movable between said respective closed and open positions into and out of ball-poppet line-contact (44, 54, 344) for sealing with said smaller-diameter end (38, 48, 238, 248, 438) of said supply valve seat
(36, 46, 236, 246, 336, 436), said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) having a chord dimension at said line-contact (44, 54, 344) with said smaller- diameter end (38, 48, 238, 248, 438) of said valve seat (36, 46, 236, 246, 336, 436) that is smaller than said larger-diameter end (40, 50, 240, 250) of said valve seat (36, 46, 236, 246, 336, 436), said frusto-conical valve seat (36, 46, 236, 246, 336, 436) having a seat angle (37, 47) relative to the centerline (57, 67) of said valve seat (36, 46, 236, 246, 336, 436) that is greater than an angle (59, 69) formed by the centerline (57, 67) of said valve seat (36, 46, 236, 246, 336, 436) and a line (56, 66) tangent to said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) at said ball-poppet line-contact (44, 54, 344) when said ball-poppet (42, 52, 242, 252, 342, 442, 452) is in said closed position, an annular space (43, 53) formed between said valve seat (36, 46, 236, 246, 336, 436) and said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) defining a restricted flow area adjacent said ball-poppet line-contact (44, 54, 344) between said spherical ball-poppet (42, 52, 242, 252, 342, 442, 452) and said smaller-diameter end (38, 48, 238, 248, 438) of said valve seat (36, 46, 236, 246, 336, 436).
2. A selector fluid control valve as claimed in claim 1, wherein said seat angle
(37, 47) relative to said centerline (57, 67) is forty-five degrees, such that an
angle between diametrically opposite portions of said valve seat is ninety
degrees.
3. A selector fluid control valve as claimed in claim 1, wherein said fluid valve passageway comprises a cylindrical cavity (60, 70) immediately adjacent of said larger-diameter end (40, 50, 240, 250) of said valve seat (36, 46, 236, 246, 336, 436), said cavity (60, 70) being larger in diameter than said larger-diameter end (40, 50, 240, 250).
4. A selector fluid control valve as claimed in claim 1, wherein said control valve (210, 410) is a pneumatic control valve and wherein said high pressure valve means and said low pressure valve means are ball-poppet valve means.
5. A selector fluid control valve as claimed in any of the preceding claims, wherein said frusto-conical valve seat (336) is located within a replaceable valve sea?: disc (388) removably disposed within said valve fluid passageway.
6. A selector fluid control valve as claimed any of the preceding claims, wherein said valve means further comprises a resilient biasing member (71, 261, 271, 361, 461) for resiliently urging said ball-poppet guide (62, 72, 262, 21%, 362, 462, 472) toward one axial end of said cavity portion.
7. A selector fluid control valve as claimed any of the preceding claims, wherein said resilient biasing member (71, 261, 271, 361, 461) is a spring wave wapher.
8. A selector fluid control valve as claimed in claim i, wherein said high-pressure working fluid and said low-pressure working fluid are pneumatic working fluids.
9. A selector fluid control valve as claimed in any of the preceding claims,
wherein said high-pressure pneumatic working fluid is at a pressure in the
range of 300 psig to 900 psig (21 bars to 62 bars).
10. A selector fluid control valve as claimed in any of the preceding claims,
wherein said high-pressure pneumatic working fluid is at a pressure of 600 psig
(41 bars).
11. A selector fluid control valve as claimed in any of the preceding claims, wherein said low-pressure working fluid is at a pressure in the range of 10 psig to 300 psig (0.7 bar to 21 bars).
12. A selector fluid control valve as claimed in any of the preceding claims, wherein said low-pressure working fluid is at a pressure of 100 psig.
13. A selector fluid control valve as claimed in any of the preceding claims, wherein said ball-poppet (42, 52, 242, 252, 342, 442, 452) is composed of a metallic material or a synthetic material.
14. A selector fluid control valve as claimed in any of the preceding claims, wherein said metallic material comprises stainless steel.
15. A selector fluid control valve as claimed in claim 4, wherein said selector fluid control valve (210, 410) supplies two different working fluid pressures to a fluid actuated device by way of a separate primary fluid control valve (10).
16. A selector fluid control valve as claimed in claim 4, wherein said selector fluid control valve (410) is made to supply more than two different working fluid pressures, further comprising two of said high -pressure inlets (420a, 420b) in respective fluid communication with two sources of pneumatic working fluid at different relatively high pressures, respectively, two of said high-pressure ball-pqppet valve means, and two of said pilot actuators (480a, 480b).
17. A selector fluid control valve substantially as hereinbefore described with reference to the accompanying drawings.

Documents:

960-delnp-2003-abstract.pdf

960-delnp-2003-claims.pdf

990-del-2001-complete specification(as files).pdf

990-del-2001-complete specification(granted).pdf

990-del-2001-correspondence-others.pdf

990-del-2001-correspondence-po.pdf

990-del-2001-description (complete).pdf

990-del-2001-drawings.pdf

990-del-2001-form-1.pdf

990-del-2001-form-18.pdf

990-del-2001-form-2.pdf

990-del-2001-form-3.pdf

990-del-2001-form-5.pdf

990-del-2001-gpa.pdf

990-del-2001-petition-124.pdf

990-del-2001-petition-137.pdf

990-del-2001-petition-138.pdf

abstract.jpg


Patent Number 242681
Indian Patent Application Number 990/DEL/2001
PG Journal Number 37/2010
Publication Date 10-Sep-2010
Grant Date 04-Sep-2010
Date of Filing 27-Sep-2001
Name of Patentee ROSS OPERATING VALVE COMPANY
Applicant Address 1250 KIRTS BLVD., TROY, MICHIGAN 48007, UNITED STATES OF AMERICA.
Inventors:
# Inventor's Name Inventor's Address
1 CHARLES ALBERT WEILER, JR. 2711 JOSSMAN, HOLLY, MICHIGAN 48442, UNITED STATES OF AMERICA.
PCT International Classification Number F16K 51/00
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 09/671,841 2000-09-27 U.S.A.