High pressure valve

ES 2 252 575 T3

DESCRIPTION

High pressure valve.

Reference to related requests

This application is a continuation in part of U.S. Patent Application No. 09 / 671,841 filed September 27, 2000, which is a continuation in part of U.S. Patent Application No. 09 / 527,395, filed March 16, 2000. Descriptions of the earlier applications are included herein by reference.

Background and summary of the invention

In general, the invention relates to fluid control valves for actuating a fluid actuation device and, more particularly, to fluid control valves that make use of one or more ball check valves.

High pressure control valves are known from EP 1134430A2 and GB 940901. Preferably, a ball check valve and a frusto-conical valve seat, adapted for substantially linear contact between them, are provided with a limited upward flow zone in order to minimize sonic flow damage to the surface. actual valve seat tightness.

Fluid control valves are often used for a wide variety of high pressure applications, such as blow molded plastic bottles or other such containers. While such control valves have generally operated satisfactorily, they often have a short life due to excessive wear caused by exposure to high fluid pressures, and may also suffer internal fluid leakage. Such internal fluid leaks, such as carry-over leaks, can occur while the inlet port of the valve is being opened and the exhaust port of the valve is simultaneously closed in order to actuate the fluid actuation device. Consequently, these factors have contributed to the high operating costs and high maintenance costs of the prior art systems.

Furthermore, in many commercial applications it is preferred that the control valve be capable of outputting various pressures. For example, with respect to blow molded plastic bottles, it is often advisable to initially introduce a relatively low pressure into the mold in order to introduce the plastic (or other material) into the molding cavity (s) and subsequently introduce a pressure relatively high to push the material or expand the material to form the mold cavity.

Accordingly, there is a need, in the relevant art, to provide a multi-pressure or high-pressure fluid control valve that is capable of minimizing wear and internal fluid leakage therefrom, in order to enhance maximize valve life and minimize related operating and maintenance costs. Furthermore, there is a need in the relevant art to provide a fluid control valve that is capable of selectively outputting various pressures to the fluid actuation device.

In accordance with the numerous teachings of the present invention, a main control valve for actuating a fluid actuated device includes a fluid inlet, a fluid outlet, and a conduit in fluid communication between the fluid inlet and the fluid outlet. , the duct defining a longitudinal axis. A valve seat is disposed in the conduit and includes a rising diameter and a falling diameter. The descending diameter is less than the ascending diameter. A ball check valve can be placed in a position of linear sealing contact with the valve seat. The valve seat has a valve seat angle, relative to a center line of the longitudinal axis, that is greater than an angle formed by the center line and a line tangent to the ball check valve at the linear contact position of seat.

Each side of the preferred frusto-conical intake valve seat has an intake seat angle, relative to the center line of the intake valve seat, that is greater than an angle formed by the center line of the intake valve seat and a line tangent to the intake ball check valve, in the above-mentioned substantially linear contact, when the intake ball check valve is in its closed position. It is preferred that the included angular relationship of the valve seat angles on both sides of the center line is approximately ninety degrees. This results in the formation of an annular space between the intake valve seat and the spherical, intake ball check valve, which defines a zone of intake flow limited upward from the substantially linear contact, mentioned above. , when the intake ball check valve is initially moved to its open position and when the high speed, high pressure moving fluid initially flows down past the intake ball check valve through the smaller diameter end valve seat. This is highly advantageous because any sonic flow erosion caused by the initial flow of high-speed, high-pressure motor flow through the annular zone of limited intake flow travels substantially just up to a rising surface of the intake valve seat. which is adjacent to said annular zone of limited intake flow. Most importantly, such a rising surface of the intake valve seat is an area that the intake ball check valve does not contact tightly. Thus, such immediate displacement of the zone susceptible to sonic damage substantially minimizes sonic erosion of the smaller diameter, almost "blade" -type, downstream end of the intake valve seat that is substantially in-line contacted by the valve. intake ball check. In control valves according to the present invention having both intake valve systems and exhaust valve systems, it is preferred to provide a similar arrangement in the exhaust conduit in fluid communication for fluid escape between the charge outlet conduit ( and load outlet) and the exhaust outlet. As mentioned above, this arrangement is also applicable to a pressure selector fluid control valve, as described below.

Furthermore, the present invention preferably includes a generally cylindrical cavity just ha3

ES 2 252 575 T3 above the larger diameter rising ends of the intake and / or exhaust valve seats, said cavity preferably having a larger diameter than the larger diameter rising end of the respective valve seats. A cylindrical check valve guide or ball check valve guide is located in said enlarged diameter cavity of the fluid conduit, the ball check valve guide having a central guide bore extending axially therethrough. A series of circumferentially spaced axially extending guide tabs protrude radially inward of the guide bore, the ball check valve accommodating within the guide bore for axial movement within the radially inward edges of the guide tabs, between its open position and its closed position. The inside diameter of the cavity mentioned above is preferably slightly larger than the outside diameter of the ball check valve guide, in order to allow both the ball check valve guide and the check valve balls float radially within the cavity. This allows the generally spherical ball check valve to be centered for substantially linear sealing contact with the smaller diameter end of the respective intake or exhaust valve seat. Said circumferentially spaced guide tabs allow high pressure motor flow to flow between them and the ball check valve guide substantially minimizes ball check valve and / or valve seat wear that would result if it could. vibrate or move radially in the fluid flow at high speed. Such a ball check valve guide can also be used in a selector fluid control valve, as will be described later.

Likewise, the present invention substantially prevents pass-through leakage of high pressure fluid control valves, which have both intake and exhaust valve systems, by activating the actuator of the exhaust ball check valve, thereby closing. mode the exhaust side of the control valve just before activating the intake ball check valve actuator, which subsequently opens the intake side and initiates an intake flow to the charging duct and orifice.

The ball check valves mentioned above (either for main valves or selector fluid control valves) are preferably composed of a metallic material, such as, for example, stainless steel, and the valve guides Ball check retainers mentioned above are preferably composed of a synthetic material, such as, for example, nylon. Those skilled in the art will readily recognize that use may also be made of other metallic materials, synthetic or non-synthetic, for ball check valves and / or ball check valve guides, depending on the specific motive fluid ( pneumatic or liquid) that is used, depending on the presumed specific pressures of the motor fluid, as well as depending on the specific application in which the fluid control valve of the present invention is used.

The present invention also provides a pressure selector fluid control valve for selectively supplying at least two different motive fluid pressures to a fluid actuated device, either directly or via a main fluid control valve, such as the one discussed above. An example of a selector fluid control valve according to the present invention preferably has a high pressure inlet in fluid communication with a source of motor fluid at a relatively high pressure, a low pressure inlet in fluid communication with a relatively low pressure source of motive fluid and an interconnected charging fluid outlet conduit in fluid communication with the fluid actuated device or with the main fluid control valve inlet . Such a selectorized fluid control valve further includes a normally closed high pressure valve mechanism in fluid communication between the high pressure inlet and the charging fluid outlet conduit to selectively allow the fluid to high pressure flow from the high pressure inlet to the charging fluid outlet conduit, as well as a low pressure, normally open valve mechanism, in fluid communication between the low pressure inlet and the charging fluid outlet conduit, to selectively allow low pressure fluid to flow from the low pressure inlet to the charging fluid outlet conduit. An auxiliary actuator is provided and can be selectively actuated to bias the normally closed high pressure valve mechanism to an open position and allow said high pressure fluid to flow from the high pressure inlet to the outlet fluid conduit. load. Said high pressure fluid admitted to the charging fluid outlet conduit pushes the normally open low pressure valve mechanism to a closed position to prevent fluid from flowing between the low pressure inlet and the charging fluid outlet conduit. . Therefore, selective actuation or activation of the auxiliary actuator, be it high pressure or low pressure motive fluid (such as, for example, a pneumatic motive fluid), can be admitted at the input of a fluid actuated device or at the inlet of a main fluid control valve, such as that described above, or virtually any type.

At least one or, preferably, both of the high pressure and low pressure valve mechanisms may include a valve seat, generally frusto-conical, located in a fluid valve conduit in fluid communication with the charging fluid outlet conduit. , the valve seat having a lower diameter downstream end and a larger diameter upstream end. A ball check valve, generally spherical, can be selectively moved between respective closed and open positions in and out of substantially linear sealing contact of the ball check valve with said smaller diameter end of the intake valve seat. . The generally spherical ball check valve preferably has a chord dimension, in said linear contact with the smaller diameter downstream end of the valve seat, which is smaller than the larger diameter upstream end of the valve seat. The valve seat, generally frustoconical, preferably has a seat angle

ES 2 252 575 T3 with respect to the center line of the intake valve seat which is greater than an angle formed by the center line of the valve seat and a line tangent to the ball check valve, spherical, in the linear contact of the ball check valve when the ball check valve is in said closed position, preferably said seat angle being approximately forty-five degrees, such that the total seat angle between diametrically opposed valve seat portions is approximately ninety degrees. Therefore, an annular space formed between the valve seat and the ball, spherical check valve, defines a zone of limited flow upward of the linear contact of the ball check valve between the ball, spherical check valve. , and the smaller diameter downstream end of the valve seat when the ball, spherical, check valve it initially moves out of said linear contact to its open position and as motor flow initially flows down past the ball check valve through the smaller diameter end of said valve seat. With such an arrangement, any sonic flow erosion, caused by the initial flow of motive fluid past the open ball check valve, travels substantially just into an upstream zone of the valve seat that is adjacent to the zone limited flow and that the ball check valve, spherical, does not contact tightly. This substantially minimizes the sonic damage caused to the smaller diameter downstream end of said valve seat, against which the ball check valve is tightly engaged when in its closed position. This greatly increases the life of the control valve by minimizing wear on the sealing portion of the valve seat.

One or both of the fluid valve conduits may include a generally cylindrical cavity just upstream of the larger diameter rising end of the valve seat, the cavity having a larger diameter than the larger diameter rising end. Preferably, the valve mechanism includes a generally cylindrical ball check valve guide located in the cavity of said fluid conduit, the ball check valve guide having a central guide bore extending axially through it. . Preferably, the ball check valve guide has a series of axially extending, circumferentially spaced guide tabs that protrude radially inward of the guide bore, the ball check valve being housed within the guide bore for movement. axially into the edges, radially inward, of the guide tabs between their open position and their closed position. The inside diameter of the cavity is larger than the outside diameter of the ball check valve guide in order to allow the ball check valve guide to float radially within the cavity and to allow the ball check valve , spherical, is substantially centered for linear sealing contact with the smaller diameter end of said frusto-conical valve seat.

An example of a selectorized fluid control valve in accordance with the present invention may further include a high pressure inlet in fluid communication with a source of motor flow at a relatively high pressure, a low pressure inlet in fluid communication with a relatively low pressure motor flow source and an interconnected charging fluid outlet conduit in fluid communication with the fluid actuated device or with the main fluid control valve inlet, It has a control stem that can be selectively adjusted. The control stem selectively adjusts to a plurality of positions, including a closed position, a fully open position, and a plurality of positions intermediate between them to limit the flow of motive fluid through the low pressure inlet.

In any of the main or pressure selector fluid control valves in accordance with the present invention, the frusto-conical valve seat may alternatively be located in a replaceable valve seat disc that is of a harder material than that of the valve body. valve.

Additional objects, advantages, and features of the present invention will become apparent from the following description and the appended claims when considered in conjunction with the accompanying drawings.

From the detailed description, which is provided later in the present specification, other areas of applicability of the present invention will become apparent. It should be understood that the detailed description and specific examples, while indicating the preferred embodiment of the invention, are only intended to illustrate it and are not intended to limit the scope of the invention.

Brief description of the drawings

The present invention will be better understood from the detailed description and accompanying drawings, in which:

Figure 1 is a cross-sectional illustration of an example fluid control valve in accordance with the present invention.

Figure 2 is an end view of the fluid control valve of Figure 1.

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 a top view of a ball check valve guide for use with either or both of an intake ball check valve and an exhaust ball check valve of the control valve of Figure 1 .

Figure 5 is a side view of the check valve guide of Figure 4.

Figure 6 is an enlarged detailed view of the intake valve system portion of the control valve of Figure 1, showing the intake ball check valve in its closed position.

Figure 7 is an enlarged detailed view similar to Figure 6, but illustrating the intake ball check valve in its initially open state.

Figure 8 is an enlarged detailed view of the exhaust valve system portion of the control valve of Figure 1, showing the exhaust ball check valve in its closed position.

Figure 9 is an enlarged detailed view similar to Figure 8, but illustrating the

ES 2 252 575 T3 exhaust bowl check valve in its initially open state.

Figure 10 is a cross-sectional illustration of an example of a two pressure selector fluid control valve in accordance with the present invention.

Figure 10a is a cross-sectional view taken generally along line 10a-10a of Figure 10.

Figure 11 is a top view of the example two-pressure selector fluid control valve of Figure 10, operatively interconnected with a main fluid control valve, as illustrated in Figures 1 through 9, both being mounted on a fluid manifold.

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-sectional illustration of an example pressure selector fluid control valve similar to Figure 10, but showing an alternate three pressure version of the selector fluid control valve.

Figure 15 is an enlarged detailed view of an alternative version of the ball check valve portion of a control valve, according to the invention, having a replaceable valve seat disc and which is applicable to any of the fluid control valves of Figures 1 through 14 and

Figure 16 is a cross sectional illustration of an example two pressure selector fluid control valve including an adjustable control stem in accordance with the present invention.

Detailed description of the preferred embodiments

The following description of the preferred embodiments is by way of example only and is in no way intended to limit the invention, its application or uses.

Referring to Figure 1, an example of a main fluid control valve 10 is shown having a body 12, an auxiliary cap 14, and a manifold 16. The body 12 and auxiliary cap 14 are attached to the manifold 16 by means of a series of bolts 18. However, it should be understood that body 12 and auxiliary cap 14 may be coupled together via fluid lines, without the use of manifold 16, if tapped holes are alternatively provided.

The exemplary main control valve 10 includes an inlet port 20, an outlet or charge port 22, and an exhaust port 24. A motive fluid intake conduit 28 provides the motive fluid with communication from the inlet port 20 to the outlet port 22, which is connected, such as via manifold 16, to a fluid actuated device. Similarly, an exhaust conduit 30 provides the exhaust fluid with communication between the charging port 22 and the exhaust outlet 24.

In the example main control valve 10, the intake and exhaust passages 28 and 30, respectively, include a frusto-conical intake valve seat 36 and a frusto-conical exhaust valve seat 46. The intake valve seat 36 includes a smaller diameter end 38 and larger diameter end 40. Similarly, the exhaust valve seat 46 includes a smaller diameter end 48 and a larger diameter end 50. A generally spherical intake ball check valve 42 and a similar generally spherical exhaust ball check valve 52 are provided for opening and closing movement relative to their frusto-conical intake and exhaust valve seats. 36 and 46 respectively.

Preferably, the intake ball check valve 42 is movably actuated by means of an auxiliary intake actuator 80, which receives auxiliary air from an auxiliary air passage 97, which, in turn, is connected in fluid communication with an auxiliary air inlet 96. When the auxiliary intake actuator 80 is activated, the force of the auxiliary air is transmitted to the intake piston 81 and, in turn, to the intake tappet 82 to separate the intake ball check valve 42 from the intake valve seat. 36, thereby opening the intake valve system portion of the control valve 10. When the auxiliary intake actuator 80 is deactivated, the ball check valve 42 returns to its closed position under the influence of inlet fluid pressure and a return spring 58.

Likewise, by activating an auxiliary exhaust actuator 90, the exhaust ball check valve 52 is urged to its closed position relative to the exhaust valve seat 46. In this regard, the auxiliary actuator 90 acts to apply the pressure. auxiliary air force on an exhaust piston 91 and in turn eject pusher 98 (Fig. 1) toward exhaust ball check valve 52. Upon deactivating the auxiliary exhaust actuator 90, the exhaust ball check valve 52 is pushed back to its open position under the influence of the high pressure motive fluid in the exhaust conduit 30.

One skilled in the art will readily recognize that, alternatively, use may be made of actuators other than the exemplary electro-pneumatic intake auxiliary actuator 80 and the electro-pneumatic exhaust auxiliary actuator 90. Actuators of this type could include, for example, electromechanical solenoids, whether local or remote, mechanical motion transmission devices, or a wide variety of other actuators well known to those skilled in the art.

Referring primarily to Figures 6 and 7, the exemplary high pressure fluid control valve 10 which is depicted in the drawings also preferably includes a generally cylindrical intake cavity 60 just upstream of the larger riser end. diameter 40 of intake valve seat 36. As illustrated in Figures 4 through 6, a generally cylindrical intake check valve guide 62 is provided upstream of the preferably cylindrical, diametrically elongated intake cavity 60. Intake check valve guide 62 includes a generally cylindrical central intake guide bore 64 extending axially therethrough, with a series of axially spaced circumferentially spaced and axially extending intake guide tabs 66 protruding radially inward. intake guide bore 64. Intake ball check valve 42 is housed within intake guide bore 64

ES 2 252 575 T3 for axial movement within the edges, radially inward, of the intake guide tabs 66 between their closed position and their open position, relative to the intake valve seat 36. As perhaps best illustrated in Figures 6 and 7, the inside diameter of the intake cavity 60 is slightly larger than the outside diameter of the intake ball check valve guide 62, thereby allowing the valve guide to check valve 62 and ball check valve 42 float radially within intake cavity 60. As such, the generally spherical intake ball check valve 42 is centered for substantially linear sealing contact 44 with the smaller diameter end 38 of the intake valve seat 36.

In addition, the intake guide tabs 66 preferably extend axially downward to form an intake guide tab extension portion 63 at one end of the intake check valve guide 62. A resilient ring 61, such As an O-ring, it surrounds the extension portion 63 in order to resiliently push the check valve guide 62 toward the opposite upstream end of the intake cavity 60. This action results from the compression of the resilient ring 61 between the floor of the intake cavity 60 and the remainder of the intake ball check valve guide 62.

It should be noted that the foregoing arrangement, as depicted in Figures 4-7, is substantially normal to the frusto-conical exhaust valve seat 46. Explained in more detail, the smaller diameter riser end 48 is arranged to mesh, in substantially linear contact with the generally spherical exhaust check valve 52 shown in Figure 1. The intake check valve guide 62 shown in Figures 4 and 5 is also substantially normal for the exhaust check valve guide 72, which is housed within the generally cylindrical, diametrically elongated exhaust cavity 70 and It has a similar exhaust guide center bore 74 and similar exhaust guide tabs 76, and which can also be seen in Figures 1, 8 and 9.

In particular, referring to Figures 6 and 7, there is shown an enlarged detailed view of the intake valve system portion of the example control valve 10. In Figure 6, the ball check valve 42 is shown. shown in its closed position, in which the ball check valve 42 is engaged, tightly in substantially linear contact 44, with the edge of the smaller diameter end 38 of the intake valve seat 36. Similarly, in Figure 7 the ball check valve 42 is shown partially open and therefore displaced from said substantially linear contact 44. The frusto-conical intake valve seat 36 preferably has a valve seat angle 37 (relative to the center line 57 of the valve seat 36) that is slightly greater than the tangent angle 59 of the tangent line 56 to the valve. ball check 42 (relative to center line 57) when ball check valve 42 is in substantially linear contact 44, as shown in Figure 6.

This valve seat arrangement results in an annular space 43 that creates a limited intake flow zone just above the intake linear contact 44 and the smaller diameter end 38. The limited flow zone is created when the intake ball check valve 42 initially moves from said linear contact 44 to its open position, as shown in Figure 7, as the motive fluid flows downward past the valve. ball check valve 42 through the smaller diameter end 38 of the intake valve seat 36. Accordingly, any sonic flow erosion damage, caused by said initial flow of high-pressure motive fluid, travels substantially right up to an upward zone 45 of the intake valve seat 36. This is highly advantageous in that it displaces such wear or damage. caused by such erosion by sonic flow to an area of ​​the intake valve seat 36 that is adjacent to the annular space 43 rather than in contact with the ball check valve 42. Accordingly, the sonic damage caused to the smaller diameter downstream sealing end 38 of the intake valve seat 36 is minimized. Accordingly, the damage caused to the actual sealing surface of the valve seat is also substantially minimized. 36 of the ball check valve 42, as well as the wear of the same and the functional life of the control valve 10, for example, is prolonged to the same extent. In this regard, the downtime and maintenance costs associated with a system using a control valve 10 according to the present invention are reduced.

As one skilled in the art will readily recognize, the function of the ball check valve 42, described above, relative to the intake valve seat 36, as shown in Figure 6 and Figure 7, is similar. to the function and relationship of the exhaust ball check valve 52 and the exhaust valve seat 46.

Referring primarily to Figures 8 and 9, the exemplary high pressure fluid control valve 10, which is depicted in the drawings, preferably also includes a generally cylindrical exhaust cavity 70 just downstream of the end. larger diameter downstream 50 from exhaust valve seat 46. A generally cylindrical exhaust check valve guide 72 (similar to the intake check valve guide 62 of Figures 5 and 6) is provided downstream of the preferably diametrically elongated cylindrical exhaust cavity 70. The exhaust check valve guide 72 includes a central exhaust guide bore, generally cylindrical, 74 extending axially therethrough, with a series of circumferentially spaced and axially extending exhaust guide tabs 76 protruding radially inward. of the exhaust guide bore 74. The exhaust ball check valve 52 is housed within the exhaust guide bore 74 for axial movement within the edges, radially inward, of the exhaust guide tabs 76 between their closed position and their open position, relative to exhaust valve seat 46. The inside diameter of the exhaust cavity 70 is slightly larger than the outside diameter of the exhaust ball check valve guide 72, thereby allowing the check valve guide 72 and the exhaust ball check valve to

ES 2 252 575 T3 float radially within exhaust cavity 70. Consequently, the generally spherical exhaust ball check valve 52 is centered for substantially linear sealing contact 54 with the smaller diameter end 48 of the seat. exhaust valve 46.

The exhaust guide tabs 76 preferably extend axially upward to form an exhaust guide tabs extension portion 73 in the exhaust check valve guide 72. A resilient ring 71, such as an O-ring, surrounds the extension portion 73 in order to push the check valve guide 72 toward the opposite downstream end of the exhaust cavity 70. This action results from the compression of the resilient ring 71 between the floor of the exhaust cavity 70 and the remainder of the exhaust ball check valve guide 72.

In particular, referring to Figures 8 and 9, a detailed view on an enlarged scale of the part of the exhaust valve system of the example control valve 10 is shown. In Figure 8, the exhaust ball check valve 52 is shown in its closed position, in which the ball check valve 52 is tightly engaged in substantially linear contact 54 with the edge of the smaller diameter end 48 of the exhaust valve seat 46. Similarly, in Figure 9 the ball check valve 52 is shown partially open and therefore displaced from said substantially linear contact 54. The frusto-conical exhaust valve seat 46 preferably has an exhaust valve seat angle 47 (relative to the exhaust center line 67 of the valve seat 46) that is slightly greater than the exhaust tangent angle 69 of the line. exhaust tangent 65 to ball check valve 52 (relative to center line 67) when ball check valve 52 is in substantially linear contact 54, as shown in Figure 8.

This valve seat arrangement results in an annular space 53 that creates a zone of limited exhaust flow just downstream of the linear exhaust contact 54 and the smaller diameter end 48. The limited flow zone is created when the exhaust ball check valve 52 initially moves from said linear contact 54 to its initially open position, as shown in Figure 9, when the exhaust fluid flows downward past the ball check valve 52 through the smaller diameter end 48 of the exhaust valve seat 46. Accordingly, any sonic flow erosion damage, caused by said initial flow of high pressure exhaust fluid, is substantially displaced just into an upflow zone adjacent to exhaust valve seat 46. This is highly advantageous because it displaces said wear or damage, caused by such sonic flow erosion, down to annular space 53 instead of contacting ball check valve 52. Accordingly, the sonic damage caused to the smaller diameter rising sealing end 48 of the exhaust valve seat 46 is minimized. Accordingly, the damage caused to the actual sealing surface of the valve seat is also substantially minimized. 46 of the ball check valve 52, as well as the wear of the same and the functional life of the control valve 10, for example, is prolonged to the same extent.

Preferably, the valve seat 46 is made of a rigid metal, such as, but not limited to, stainless steel. In this regard, the downtime and maintenance costs associated with a system using a control valve 10 according to the present invention are reduced.

Referring primarily to Figure 1, the carry-over leak of the example fluid control valve 10, which is depicted in the drawings, is substantially minimized by activating the auxiliary exhaust actuator 90 to close the check valve of the fluid. exhaust ball 52 just a moment before activating the intake auxiliary actuator 80 to open the ball check valve 42. Due to the equipment and energy required to raise the working fluid to such a high pressure state, minimizing the carry-over leak greatly reduces operating costs that would otherwise result from excessive leakage or leakage of engine fluid. high pressure. Such high pressure moving fluid, which may be pneumatic or hydraulic, but is preferably pneumatic, often ranges from 300 psig to 900 psig and is typically about 600 psig in blow molding processes that have been used. previously mentioned.

Finally, either or both of the ball check valves 42 and 52 are preferably composed of a metallic material, such as stainless steel or other metallic or non-metallic materials that a person skilled in the art considers advantageous for a particular application. Similarly, the intake ball check valve guide 62 and the exhaust ball check valve guide 72 or both are preferably composed of a synthetic material, such as nylon, but may also be composed of a metallic material, such as stainless steel or other suitable materials known to those skilled in the art.

Figures 10-15 illustrate various versions of a selector fluid control valve that can be used alone or in conjunction (on the intake side) with the main fluid control valve previously discussed in connection with Figures 1 to 9. Since many of the valve components illustrated in Figures 10 to 15 are identical or substantially similar, at least with respect to function, to those of the valves depicted in Figures 1 to 9, said valve components Figures 10 to 15 are indicated by reference numerals that are the same as Figures 1 to 9, but are prefixed with two hundred, three hundred or four hundred.

In Figures 10 through 13 an example of a selector fluid control valve 210 includes a body 212, an auxiliary cap 214, and a manifold 216 (as shown in Figures 11 through 13). Body 212 and auxiliary cover 214 are attached to manifold 216 in a manner similar to that shown above in connection with Figures 1 to 9.

The subject of claim 1 does not comprise the selectorized fluid control valve 210 illustrated in Figures 10 to 13. However, it should be understood that the body 212 and the auxiliary cap 214 can be coupled together via tubing. of fluid, without the use of manifold 216, if tapped holes are alternatively provided.

The sample selector fluid control valve 210 includes inlet ports 220 and 221, which

ES 2 252 575 T3 are in fluid communication with independent sources of motive fluid. Inlet port 220 is configured to communicate with fluid at a relatively higher pressure while outlet port 221 is configured to communicate with fluid at relatively lower pressure. In the present specification such relatively higher pressures will be referred to as "high pressure" and, likewise, such relatively lower pressures will be referred to as "low pressure". It should be understood that the inlet and outlet ports described herein may alternatively be threaded.

A charging fluid outlet conduit 228 extends through the body 212 of the selector fluid control valve 210 and is in fluid communication with an outlet charging port 222. The selector fluid control valve 210 is It may be used alone or in combination with a main fluid control valve, such as the main fluid control valve 10 of Figures 1 through 9. In such an application, the selectorized fluid control valve 210 may have its outlet charging port 222 interconnected in fluid communication with the inlet port 20 of the main fluid control valve 10, either via pipe lines. fluid or via manifold 216 of Figure 11.

Selector fluid control valve 210 also includes a normally closed, high-pressure valve mechanism in fluid communication between high-pressure inlet port 220 and charging fluid outlet conduit 228. Likewise, a The normally open low pressure valve mechanism is in fluid communication between the low pressure inlet port 221 and the charging fluid outlet conduit 228. In the selector fluid control valve example 210, the high pressure valve mechanism includes a frusto-conical valve seat 236 which, in turn, includes a smaller diameter end 238 and a larger diameter end 240. A ball check valve 242, preferably having a generally spherical shape and configuration, engages the valve seat 236 in a substantially linear contact gear, in a manner previously explained in more detail in connection with the valve seat. 36 and the ball check valve 42 of Figures 1 to 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 check valve 252 engaging the smaller diameter end 248 on the same type of linear contact discussed above.

The high pressure ball check valve 242 is housed within a high pressure ball check valve guide 262 similar to the ball check valve guide 62 of Figures 1-9. Low pressure ball check valve 252 is housed within a low pressure ball check valve guide 272. Guides 262 and 272 maintain the ball check valve's radial float and centering capabilities, related to guides 62 and 72 of Figures 1 through

9. Conversely, however, tabs 266 and 276 do not necessarily extend axially beyond the end of their respective guides 262 and 272, as do tabs 66 and 76 of guides 62 and 72, discussed above. In such an arrangement, instead of the O-rings 61 and 71 of Figures 1 to 9, resilient wave washers or spring wave washers 261 and 271 are provided to resiliently bias the respective guides 262 and 272 into their proper positions. within respective guide bores 264 and 274. However, in substantially all other respects, the ball check valve guides 262 and 272 act in a manner substantially identical to the corresponding ball check valve guides 62 and 72 discussed above.

In the preferred selectorized fluid control valve 210, the high pressure ball check valve 242 is biased to its normally closed position by means of a return spring 258 which acts on the ball check valve 242 by means of a 275 ball check valve rod. An auxiliary actuator 280 is provided in connection with the high pressure ball check valve 242 and can be selectively actuated to remove the ball check valve 242 from its respective valve seat 236 and to place it in its open position by actuation of the auxiliary actuator 280 through high pressure actuator piston assembly 281 and pusher 282.

In the low pressure valve mechanism, the ball check valve 252 is in a normally open position under the influence of the low pressure motive fluid from the low pressure inlet 221 which acts on the ball check valve 252 and against the biasing force of a low force retaining spring 251. The low pressure ball check valve 252 is held in place by a check plug 249 having a generally U-shaped opening 278 extending therethrough, as illustrated in Figure 10a. The opening stroke of the low pressure ball check valve 252 is limited by its contact with a stopper rod or pin 277 fixedly interconnected with the check plug 249 and extending into the check plug passageway 278.

In operation, selector fluid control valve 210 can be used to selectively supply one of two different pressures of motive fluid (preferably, an air motor fluid) to a fluid-actuated device or to the inlet of a main control valve ( such as the main fluid control valve 10 discussed above) via the outlet charging port 222 of the selector fluid control valve 210. Initially, a relatively low pressure source of motive fluid is supplied to the low pressure inlet port 221 and passes through the normally open ball check valve 252 to the charging fluid outlet conduit 228 and to the charging fluid port. exit 222. Such a relatively low pressure motive fluid exerts a sufficient force on the low pressure ball check valve 252 to hold it in its open position against the biasing force of the low pressure check spring 251, as long as the fluid is flowing into the valve. circuit. Therefore, in this condition, as illustrated in Figure 10, the relatively high pressure motive flow, supplied to the high pressure inlet port 220, is isolated from the pre8 motive fluid.

ES 2 252 575 T3 relatively low pressure of the charging fluid outlet conduit 228 by means of the normally closed high pressure ball check valve 242. The normally closed high pressure ball check valve is pushed against its seat of respective valve 236 under the influence of the return spring 258. In this condition, said relatively low pressure motive fluid is supplied to the outlet charging port 222.

However, when it is desired to admit relatively high pressure motive fluid into the charging fluid outlet conduit 228 and the outlet charging port 222, the auxiliary actuator 280 is selectively activated. It should be noted that the auxiliary actuator 280 can be actuated, for example, pneumatically, electrically or mechanically.

Activation of auxiliary actuator 280 causes piston assembly 281 and plunger 282 to push high pressure ball check valve 242 to its open position against the biasing force of return spring 258 and the high pressure fluid from the valve. entry 220. This opening of the high pressure ball check valve 242 allows relatively high pressure motive fluid from the high pressure inlet port 220 to enter the charging fluid outlet conduit 228. The high pressure motive fluid admitted to the charging fluid outlet conduit 228 acts (in conjunction with the low force check spring 251) to push the normally open low pressure ball check valve 252 to its closed position in a sealed gear with valve seat 246. Therefore, in this condition, the relatively low pressure motive fluid of the low pressure inlet port 221 is isolated from the relatively high pressure motive fluid of the charging fluid outlet conduit 228, the check plug conduit 278, and outlet charging port 222. As mentioned above, this allows a selective delivery of either the relatively low pressure motive fluid or the relatively high pressure motive fluid from the outlet charging port 222 to a fluid actuated device or to the inlet 20 of a main valve, such as the main control valve 10 illustrated in Figures 1 through 9. This latter arrangement is illustrated in Figures 11 to 13, in which selector fluid control valve 210 and main control valve 10 are mounted together on manifold 216. Once again, manifold 216 can be replaced, alternatively, by separate fluid lines if alternative tapped holes are provided.

In Figure 14, an alternative embodiment of a selector fluid control valve according to the present invention is represented, in order to illustrate that the present invention is equally applicable to control valves of this type adapted to supply more than two motive fluid pressures other than a fluid actuation device, either directly or through a main fluid control valve, such as the main fluid control valve 10 discussed above and shown in Figures 1-9. The selector fluid control valve 410 of Figure 14 has several components that are identical or functionally substantially similar to those of the selector fluid control valve 210 in Figure

10. However, in Figure 14 said equivalent components are indicated by reference numerals having the prefix four hundred or the suffixes a or b in the case of components that are identical to each other.

The body 412 of the selector fluid control valve 410 includes two of the high pressure inlets 420a and 420b, which have been discussed above, with two of the auxiliary actuators 480a and 480b, which have been described above, each of which can be actuated independently or selectively to push their respective ball check valves 442a and 442b to their respective open positions. However, in virtually all other respects, selector fluid control valve 410 functions in substantially the same way as selector fluid control valve 210 described above.

The difference in operation between the selector fluid control valve 410 and the selector fluid control valve 210 is that the auxiliary actuators 480a and 480b can be independently or selectively actuated or activated, or switched off or deactivated, as required. in order to allow the selective supply of three different pressures or motor fluids to the fluid actuated device, via the outlet charging port 422, either directly or via the main fluid control valve, mentioned above. It should be noted that Figure 14 only illustrates one example of the various pressure application of the present invention and one skilled in the art will readily recognize that the selector fluid control valve of the present invention can accommodate any number of different pressures. .

In Figure 15, yet another alternative arrangement of the present invention is depicted, in which the resilient elastic wave washer 361 is moved to an opposite position, relative to the ball check valve guide, which is depicted in Figure 10. In this arrangement, a replaceable valve seat disc 388, including valve seat 336 therein, is retained between ball check valve guide 362 and the downward end of guide bore 364. Valve seat 388 includes a beveled edge 386 which is sealingly engaged by means of an O-ring 384 and which is preferably composed of a harder material than the valve body. Such an arrangement allows for proper replacement of a worn valve seat 336 simply by replacing the valve seat disc 388, without the need to scrap or re-machine the valve seat 236 of the body 212 of Figure 10. Therefore, a selector fluid control valve can be partially disassembled and repaired with such replacement of valve seat disc 388 while another selector fluid control valve is in operation. Such a repaired selector fluid control valve can be reserved for immediate replacement of a worn selector fluid control valve that is currently in operation. It should be noted that a similar replaceable valve seat disc may also alternatively be used in conjunction with any of the valve arrangements or mechanisms shown in Figures 1-15.

Finally, the fluids or the preferred high pressure air motor fluid may be at virtually any pressure greater than that of the motor fluid of the engine.

ES 2 252 575 T3 low pressure, such as, for example, pressures ranging from 300 psig to 900 psig, an application requiring a high pressure moving fluid at approximately 600 psig. Similarly, the low pressure moving fluid can be at virtually any pressure lower than that of the high pressure moving fluid, such as, for example, pressures ranging from 10 psig to 300 psig, requiring at least one application, said low pressure moving fluid at a pressure of approximately 100 psig. Furthermore, as mentioned above, the main fluid control valves and selector control valves of the present invention have a wide range of applicability in various pneumatic or liquid fluid control or actuation systems. An example of such an application is a pneumatic system for blow molding plastic bottles or other containers, which requires a relatively lower first pressure to introduce the plastic material into the molding cavity, followed by a relatively high pressure motor fluid. larger to complete the blow molding procedure by pushing the plastic material against the internal contours of the mold. However, one skilled in the art will readily recognize that this is only one example of the many applications of the present invention.

Returning to Figure 16, an alternate embodiment of the selector fluid control valve in accordance with the present invention is shown. The selector fluid control valve 610 of Figure 16 has several components that are identical or functionally substantially similar to those of the selector fluid control valve 210 of Figure 10. However, in Figure 16 said equivalent components are indicated with reference numerals prefixed by five hundred, in the case of components that are identical to each other. In addition, the components for the selector valve 610 incorporating an adjusting stem 602 are indicated by numerals prefixed with six hundred.

The body 512 of the selector fluid control valve 510 includes the high pressure inlet 520, which has been discussed above, with the auxiliary actuator 580, which has been described above, which can be selectively actuated to push the check valve. ball 542 to its respective open position. It should be noted that wave springs 561 and 571 have moved to opposite sides of ball check valves 542 and 552. In addition, as will be explained in more detail later, the normally open low-pressure ball check valve 552 cooperates with the fluid control adjusting stem 602. In virtually all other respects, however, the flow control valve selector fluid 610 operates in substantially the same way as the previously described selector fluid control valve 210.

Still referring to Figure 16, the fluid control adjusting stem 602 is linearly actuated, selectively, through the bore 604 by turning the flow control knob 606. In this regard, the linear stroke of the stem Fitting 602 is bounded between surfaces 608 and 612 by sleeve 611. Plug 616 includes threads 624 to cooperate with mating threads 618 on fitting stem 602. Fasteners 626 threadably secure plug 616 to auxiliary cap 614. A locknut 640 and washer 642 are positioned between control knob 606 and auxiliary cap 614. Locknut 640 engages threads 622 to lock stem 602 to the pilot cap 614. A pin or gear portion 630 extends from a distal end of adjusting stem 602 to engage ball check valve 552 and limit allowable displacement thereof. A return spring 632 is included around pin 630.

The operation of the adjusting stem 602 will now be described in more detail. The allowable flow around the ball check valve 552 is determined by the displacement of the ball check valve 552 from the valve seat 546. In this regard, the Flow rate increases when ball check valve 552 is separated from valve seat 546. The allowable displacement of the ball check valve 552 from the valve seat 546 is controlled by the position of the pin 630 extending from the adjusting stem 602. Explained in more detail, the fluid flow through the inlet port of Low pressure 521 separates ball check valve 552 from valve seat 546 by bringing it into contact with pin 630. Thus, adjusting stem 602 can be positioned in a predetermined position to obtain a desired flow rate around ball check valve 552. Once a desired flow rate is reached, locknut 640 can be advanced to engage with the auxiliary cap 614 to prevent inadvertent turning of control knob 606.

The foregoing discussion discloses and describes only example embodiments of the present invention for purposes of illustration only. A person skilled in the art will readily recognize, thanks to said analysis and thanks to the appended claims and drawings, that various changes, modifications and variations can be made thereto without departing from the scope of the invention as defined in the following claims.