Patent Description:
Cryogenic fluid is often stored in a pressurized tank. The pressure may fluctuate due to temperature variations, filling of the tank, or dispensing of fluid from the tank. The tank may include a one or more valves for (a) regulating pressure of the tank and (b) enabling fluid to be dispensed from the tank. <CIT> describes an adjustable economizer valve that does not overlap with a pressure build function. The valve seals off a pressure build outlet from an economizer connection with a seal around a pusher post disposed in a valve body. The pusher post has an internal flow path that is sealed by a floating device that can create a seal from diaphragm pressure and can open when the diaphragm pressure is removed. The floating device is a ball or a disc plate. <CIT> describes a regulator for reducing high fluid pressure. The regulator includes a diaphragm that urges a closure member to provide an opening with a valve seat to allow fluid to emerge at the required pressure. Inlet flow is deflected around the closure member by a housing to shield it from downstream fluid flow to reduce outlet pressure droop. <CIT> describes a valve for reducing the pressure of compressed gases. The opening of a gas passage is effected by bolts that can be attached to another part.

This application is defined by the appended claims. The description summarizes aspects of exemplary embodiments and should not be used to limit the claims. Other implementations are contemplated in accordance with the techniques described herein, as will be apparent upon examination of the following drawings and detailed description, and such implementations are intended to be within the scope of this application.

In an embodiment, a valve for conveying fluid disclosed herein comprises a bonnet, a body, a flexible diaphragm, a first spring, and a spindle unit. The spindle unit comprises a pin, a first seat disc, and a seat screw. The bonnet is secured to the body. The flexible diaphragm is compressed between the bonnet and the body. The first spring is disposed in the bonnet. The spindle unit is disposed in the body. The first seat disc is disposed between the pin and the diaphragm. The first seat disc and the pin define a first void. The first spring biases the diaphragm toward the first seat disc. The seat screw is engaged with the body and is slidably engaged with the pin. The seat screw and the pin define a fluid passage in fluid communication with the first void.

In another embodiment, a valve for conveying fluid comprises a bonnet, a body, a flexible diaphragm, a first spring, and a spindle unit. The bonnet is secured to the body. The body defines a first port, a second port, and a third port. The flexible diaphragm is compressed between the bonnet and the body. The first spring is disposed in the bonnet. The spindle unit is disposed in the body and comprises a pin, a first seat disc, and a seat screw. The first seat disc is disposed between the pin and the diaphragm. The first seat disc and the pin define a first void. The first spring biases the diaphragm toward the first seat disc. The seat screw is engaged with the body and slidably engaged with the pin. The seat screw and the pin define a fluid passage in fluid communication with the first void. The second port is in fluid communication with the fluid passage and third port is in fluid communication with an undersurface of the diaphragm.

In a further embodiment, a valve for conveying fluid comprises a bonnet, a body, a flexible diaphragm, a first spring, and a spindle unit. The bonnet is secured to the body. The body defines a first port, a second port, and a third port. The flexible diaphragm is compressed between the bonnet and the body. The first spring is disposed in the bonnet. The spindle unit is disposed in the body and comprises a pin, a first seat disc, a seat screw, a seat, and a second seat disc. The first seat disc is disposed between the pin and the diaphragm. The first seat disc and the pin define a first void. The first spring biases the diaphragm toward the first seat disc. The seat screw threadably engages the body and slidably engages the pin. The seat screw and the pin define a fluid passage in fluid communication with the first void. The seat is retained in the body by the seat screw and slidably engages the pin. The second seat disc is secured to the pin and sealingly engages the seat. The valve is configured to have (a) a first position where the first port and the second port are in internal fluid communication and neither the first port nor the second port are in internal fluid communication with the third port, (b) a second position where the second port and the third port are in internal fluid communication and neither the second port nor the third port are in internal fluid communication with the first port, and (c) a third position where none of the first port, the second port, and the third port are in internal fluid communication. In the first position, the second seat disc is disengaged from the seat and the first seat disc is sealingly engaged with the pin. In the second position, the second seat disc is sealingly engaged with the seat and the first seat disc is disengaged from the pin. In the third position, the second seat disc is sealingly engaged with the seat and the first seat disc is sealingly engaged with the pin.

The description that follows describes, illustrates and exemplifies one or more embodiments of the present invention in accordance with its principles. This description is not provided to limit the invention to the embodiments described herein, but rather to explain and teach the principles of the invention in order to enable one of ordinary skill in the art to understand these principles and, with that understanding, be able to apply them to practice not only the embodiments described herein, but also other embodiments that may come to mind in accordance with these principles.

The scope of the present invention is intended to cover all such embodiments that may fall within the scope of the appended claims, either literally or under the doctrine of equivalents. The specification describes exemplary embodiments which are not intended to limit the claims or the claimed inventions. Features described in the specification, but not recited in the claims, are not intended to limit the claims.

It should be noted that in the description and drawings, like or substantially similar elements may be labeled with the same reference numerals. However, sometimes these elements may be labeled with differing numbers, such as, for example, in cases where such labeling facilitates a more clear description. Additionally, the drawings set forth herein are not necessarily drawn to scale, and in some instances proportions may have been exaggerated to more clearly depict certain features. Such labeling and drawing practices do not necessarily implicate an underlying substantive purpose. Further, each of the drawings may be drawn to a different scale (e.g., the scale of <FIG> may be different than the scale of <FIG>).

Some features may be described using relative terms such as top, bottom, vertical, rightward, leftward, etc. It should be appreciated that such relative terms are only for reference with respect to the appended drawings. These relative terms are not meant to limit the disclosed embodiments. More specifically, it is contemplated that the valves depicted in the appended drawings will be oriented in various directions in practice and that the relative orientation of features will change accordingly.

As stated above, the present specification is intended to be taken as a whole and interpreted in accordance with the principles of the present invention as taught herein and understood by one of ordinary skill in the art.

<FIG> illustrate exemplary structural features of a combination regulator valve <NUM>. With reference to <FIG>, valve <NUM> has a longitudinal axis L and includes a setting portion <NUM> joined with a flowing portion <NUM>. The combination regulator valve <NUM> serves as a fluid economizer and as a fluid regulator When serving as a fluid economizer, valve <NUM> accepts fluid at a second port 13b and expels the fluid through a third port 13c. When serving as a fluid regulator, valve <NUM> accepts fluid at a first port 13a and expels the fluid through the second port 13b.

Setting portion <NUM> enables user adjustment of the one or more pressures that cause valve <NUM> to perform the regulator function and the economizer function. More specifically, setting portion <NUM> enables user adjustment via compression of a first spring <NUM>. The compression of the first spring <NUM> controls an amount of fluid pressure necessary in flowing portion <NUM> to (a) cause a diaphragm <NUM> to upwardly flex, (b) cause the diaphragm <NUM> to downwardly flex, and (c) enable the diaphragm <NUM> to occupy a neutral or flat position.

Setting portion <NUM> includes an adjustable screw <NUM>, a nut <NUM>, a ball <NUM>, a spring support <NUM>, a bonnet <NUM>, a first spring <NUM>, a bonnet screw <NUM>, and a diaphragm plate <NUM>. Screw <NUM> is threaded into the nut <NUM> and the bonnet <NUM>. One end of the screw <NUM> bears on the ball <NUM>, which is seated in the spring support <NUM>. The spring support <NUM> and the diaphragm plate <NUM> compress the first spring <NUM> therebetween.

A user may adjust the compression of the first spring <NUM> by rotating the screw <NUM> with respect to the nut <NUM> and the bonnet <NUM>. When the screw <NUM> is rotated in a first direction (e.g., clockwise), the screw <NUM> moves downward, thus pushing the ball <NUM> downward. Because the ball <NUM> is seated between the screw <NUM> and the spring support <NUM>, downward motion of the ball <NUM> and the screw <NUM> force the spring support <NUM> downward. The diaphragm plate <NUM> is seated on the diaphragm <NUM>, which generally opposes downward motion. Consequently, compression of the first spring <NUM> increases from the smaller distance between the spring support <NUM> and the diaphragm plate <NUM>. When compression of the first spring <NUM> increases, the first spring <NUM> exerts more downward force against the diaphragm plate <NUM>.

When the screw <NUM> is rotated in a second, opposite direction (e.g., counter-clockwise), the screw <NUM> moves upwards. The first spring <NUM> presses the spring support <NUM> upward until the ball <NUM> contacts the screw <NUM>. Compression of the first spring <NUM> decreases due to the increased distance between the spring support <NUM> and the diaphragm plate <NUM>. When compression of the first spring <NUM> decreases, the first spring <NUM> exerts less downward force against the diaphragm plate <NUM>.

The flowing portion <NUM> is configured to (a) enable internal fluid communication between the first port 13a and the second port 13b, (b) enable internal fluid communication between the second port 13b and the third port 13c, and (c) disable internal fluid communication between the first, second and third ports 13a, 13b, 13c. With reference to <FIG>, flowing portion <NUM> includes a body <NUM>, an o-ring <NUM>, a spindle unit <NUM>, and the diaphragm <NUM>. As shown in <FIG>, the spindle unit <NUM> includes a first seat disc <NUM> (also called a pin engager or a sealing surface engager), a guide <NUM>, a pin <NUM> (also called an extender), a seat screw <NUM>, a seat <NUM>, a washer <NUM>, a second seat disc <NUM> (also called a seat engager or a sealing surface engager), and a second spring <NUM>.

With reference to <FIG>, the bonnet screw <NUM> compresses the bonnet <NUM> against first and second outer portions of the diaphragm <NUM>. The first outer portion of the diaphragm <NUM> is compressed between the o-ring <NUM> and the bonnet <NUM>. The second outer portion is radially outward of the first outer portion and is compressed between the body <NUM> and the bonnet <NUM>. Thus, the diaphragm <NUM> discourages fluid leakage from void <NUM> and past the bonnet <NUM> at the first outer portion and at the second outer portion.

The guide <NUM> is threaded into the body <NUM> and slidably captures the seat disc <NUM>. The guide <NUM> inwardly bears on the seat disc <NUM> to longitudinally align the seat disc <NUM> along the longitudinal axis L. The seat screw <NUM> inwardly bears on the pin <NUM> to longitudinally align the pin <NUM> along the longitudinal axis L. The seat screw <NUM> is not sealingly engaged with the pin <NUM>. Void 17c is in fluid communication with void 22c via the seat screw <NUM> as will be explained in greater detail in conjunction with <FIG>. The pin <NUM> includes a valve seat <NUM> for sealingly engaging first seat disc <NUM>. Further, the seat screw <NUM> is threaded into the body and axially bears on the seat <NUM> to capture the seat <NUM> in the body <NUM>. The washer <NUM> is compressed between the seat <NUM> and the body <NUM> to discourage fluid from flowing between the body <NUM> and the seat <NUM>.

The seat <NUM> sealingly engages the second seat disc <NUM> at valve seat <NUM>. The pin <NUM> is inserted into the second seat disc <NUM> to longitudinally align the second seat disc <NUM> with the longitudinal axis L. The second seat disc <NUM> receives the second spring <NUM> to capture the second spring <NUM> between the second seat disc <NUM> and the body <NUM> and to longitudinally align the second spring <NUM> with the longitudinal axis L. An inner surface of the second seat disc <NUM> bears on the second spring <NUM>.

As stated above, the first spring <NUM> biases the diaphragm <NUM> downward. Fluid pressure in void <NUM> biases the diaphragm <NUM> upward. Additionally, with reference to <FIG>, fluid pressure in voids 17c and 18c, bears on the first seat disc <NUM> to bias diaphragm <NUM> upward. The second spring <NUM> biases diaphragm <NUM> upward, but only until the second seat disc <NUM> engages the seat <NUM>. Similarly, fluid pressure in void 13e biases diaphragm <NUM> upward, but only until the second seat disc <NUM> engages the seat <NUM>. It should be understood that the diaphragm <NUM> may be naturally biased toward the upwardly flexed position, a neutral (i.e., flat) position, or the downwardly flexed position as a result of internal stresses induced during manufacturing.

The above-described biases and fluid pressure apply force to the diaphragm <NUM> and thus determine whether the diaphragm <NUM> is upwardly flexed, downwardly flexed, or neutral. It should be appreciated that because void <NUM> has a greater area parallel to diaphragm <NUM> than voids 17c, pressure in void <NUM> influences the position of diaphragm <NUM> to a greater extent than pressure in void 17c.

Upon installation, a user cannot access the second spring <NUM> or the diaphragm <NUM> without removing the bonnet <NUM>. Thus, by rotating the screw <NUM>, the user may control the fluid pressure in voids <NUM> and 17c that causes diaphragm <NUM> to upwardly flex and the fluid pressure in voids <NUM> and 17c that enables the diaphragm <NUM> to downwardly flex. More specifically, when the user moves the screw <NUM> downward, a greater minimum amount of pressure in voids <NUM> and/or 17c is needed to cause the diaphragm <NUM> to upwardly flex and a lesser maximum amount of pressure in voids <NUM> and/or 17c enables the diaphragm <NUM> to downwardly flex. In contrast, when the user moves the screw <NUM> upward, a lesser minimum amount of pressure in voids <NUM> and/or 17c is needed to cause the diaphragm <NUM> to upwardly flex and a greater maximum amount of pressure in voids <NUM> and/or 17c enables the diaphragm <NUM> to downwardly flex.

Upon flexing downward past the neutral or flat position, the diaphragm <NUM> presses the seat disc <NUM> downward until the seat disc <NUM> sealingly engages the pin <NUM>. The spindle unit <NUM>, more specifically the second spring, <NUM>, is configured such that when the diaphragm <NUM> flexes downward, the first seat disc <NUM> sealingly engages the pin <NUM> before the second seat disc <NUM> overcomes the upward bias of the second spring <NUM> to release from seat <NUM>. By virtue of contact between the first seat disc <NUM> and the pin <NUM>, the pin <NUM> overcomes the upward bias of the second spring <NUM> and moves downward with the seat disc <NUM>.

With reference to <FIG>, when the diaphragm <NUM> downwardly flexes, the second seat disc <NUM>, which is engaged with the pin <NUM>, moves downward and away (i.e., disengages) from the seat <NUM>, which is static with respect to the body <NUM>. Upon disengagement between the seat disc <NUM> and the seat <NUM>, fluid communication between the first port 13a and the second port 13b occurs via voids 13d, 13e, 22c, 22b, and 13f. Because seat disc <NUM> sealingly engages pin <NUM>, internal fluid communication is blocked between (a) the first and second ports 13a, 13b and (b) the third port 13c through flowing portion <NUM>. Put differently, internal fluid communication only occurs between the first and second ports 13a and 13b.

As diaphragm <NUM> flexes downward, compression of at least the second spring <NUM> increases, thus increasing the upward force exerted by the second spring <NUM> against the second seat disc <NUM> and the pin <NUM>. Eventually, the upward force exerted by the second spring <NUM> will overcome the downward force applied by the first spring <NUM> against the diaphragm <NUM>, thus arresting further downward movement of the pin <NUM>.

When fluid pressure in void <NUM> flexes the diaphragm <NUM> upward past the neutral or flat position, the second spring <NUM> pushes second seat disc <NUM> against seat <NUM> such that second seat disc <NUM> occupies the closed position shown in <FIG>. Because the second seat disc <NUM> stops against seat <NUM>, pin <NUM> cannot move upward with first seat disc <NUM>. Further, fluid pressure in voids 22c, 18c, and 17c urges the first seat disc <NUM> away from the pin <NUM>.

With reference to <FIG>, fluid pressure in void <NUM> spread across the surface area of diaphragm <NUM> produces a first force. Fluid pressure in void <NUM> spread across the surface area of the topside of the first seat disc <NUM> produces a second force. Fluid pressure in void 17c spread across the surface area of the underside of the first seat disc <NUM> radially outside of the valve seat <NUM> produces a third force. When the first force overcomes the downward force of the first spring <NUM>, the diaphragm <NUM> flexes upwardly. When the third force overcomes the second force, the first seat disc <NUM> slides in the guide <NUM> and disengages from the pin <NUM>. In other words, a first minimum fluid pressure in void <NUM> spread across the surface area of the diaphragm <NUM> overcomes the downward force of the first spring <NUM> and a second minimum pressure in void 17c spread across the bottom surface area of the first seat disc <NUM> outside of the valve seat <NUM> overcomes the downward force of fluid pressure in void <NUM> spread across the top surface area of the first seat disc <NUM>. Thus, fluid communication is enabled between the second port 13b and the third port 13c via voids 13f, 22b, 22c, 18c, 17c, <NUM>, and 13q.

By virtue of the engagement between the second seat disc <NUM> and the seat <NUM>, internal fluid communication is blocked between (a) the first port 13a and (b) the second and third ports 13b, 13c. Put differently, internal fluid communication only occurs between the second and third ports 13b, 13c. The spindle unit <NUM> is configured such that when the diaphragm <NUM> flexes upward, the second seat disc <NUM> sealingly engages the seat <NUM> before the first seat disc <NUM> disengages from pin <NUM>.

A shoulder <NUM> of the bonnet <NUM> serves as a stop for the diaphragm plate <NUM>. The combination of the shoulder <NUM> and the diaphragm plate <NUM> thus prevent the diaphragm <NUM> from upwardly flexing past a certain degree, irrespective of fluid pressure.

When the diaphragm <NUM> is in the neutral or flat position, as shown in <FIG>, the diaphragm <NUM> counters the upward force of fluid pressure in void 17c to keep the first seat disc <NUM> sealingly engaged with pin <NUM>. The second spring <NUM> overcomes downward bias of the diaphragm <NUM> against the pin <NUM> and causes the second seat disc <NUM> to sealingly engage the seat <NUM>. As a result, the valve <NUM> blocks internal fluid communication between all of ports 13a, 13b, 13c.

The spindle unit <NUM> is sized and configured to for the valve seat <NUM> to sealingly bear against the bottom of the first seat disc <NUM> when the diaphragm <NUM> is in the neutral position. Additionally, the spindle unit <NUM> is configured for the second seat disc <NUM> to sealingly bear against the seat <NUM> when the diaphragm <NUM> is in the neutral position.

As shown in <FIG>, the body <NUM> defines (a) first, second, and third ports 13a, 13b, 13c and (b) voids 13d, 13e, 13f, <NUM>, <NUM>, 13i, 13j, <NUM>, <NUM>, 13n, 13p, and 13q. For the reader's convenience and to avoid confusion, the void numbering skips <NUM> and 13o.

The first, second, and third ports 13a, 13b, 13c are partially conical and transversely extending in the body <NUM>. The first and second ports 13a, 13b are opposite one another with collinear central axes. The third port 13c has a central axis perpendicular to the central axes of the first and second ports 13a, 13b.

Void 13d is cylindrical with a central axis angled with respect to the longitudinal axis L and the central axis of the first port 13a. Void 13e is cylindrical and linked to void 13a via void 13d. Void 13e has a central axis parallel to and collinear with the longitudinal axis L. Void 13e accommodates the second seat disc <NUM>, an end of the second spring <NUM>, at least a portion of the seat <NUM>, and at least a portion of the pin <NUM>. Void 13f, has a central axis perpendicular to the longitudinal axis L, has three lobes, and links the second port 13b with void 22b of the seat <NUM>.

Void <NUM> is disc shaped and accommodates at least a portion of the seat <NUM>, at least a portion of the pin <NUM>, and the washer <NUM>. Void <NUM> may be sized and configured to enable fluid in void 22b of the seat <NUM> to communicate with void 13f without passing through void <NUM>. A central axis of void <NUM> is collinear with the longitudinal axis L. Void <NUM> has a maximum diameter exceeding the maximum diameters of voids 13e and <NUM>. As shown in <FIG>, void <NUM> includes ring-shaped void <NUM>. When viewed in cross section, void <NUM> is triangular. The washer <NUM> sits directly above void <NUM>.

Void <NUM> is cylindrical. Inner surfaces of the body <NUM> defining void <NUM> are threaded to threadably engage with the seat screw <NUM>. A central axis of void <NUM> is parallel to the longitudinal axis L. Void <NUM> accommodates the threaded portion of the seat screw <NUM> and at least a portion of the pin <NUM>. Void 13i is a conical transition between voids <NUM> and 13j. Void 13i has a larger major diameter than the non-threaded portion of void <NUM> and a central axis collinear with longitudinal axis L.

Void 13j is cylindrical. Inner surfaces of the body <NUM> defining void 13j are threaded to threadably engage with the guide <NUM>. A central axis of void 13j is parallel to the longitudinal axis L. Void 13j accommodates at least portions of the guide <NUM>, the pin <NUM>, and the first seat disc <NUM>. Void <NUM> is cylindrical with a central axis collinear with the longitudinal axis L. Void <NUM> has a greater diameter than any of voids 13e, <NUM>, <NUM>, 13i, and 13j. Void <NUM> accommodates at least portions of the guide <NUM> and the first seat disc <NUM>. When downwardly flexed, the diaphragm <NUM> protrudes into void <NUM>.

Void <NUM> is cylindrical with a central axis collinear with the longitudinal axis L. A portion of the inner surfaces of the body <NUM> defining void <NUM> are threaded to threadably engage with the bonnet screw <NUM>. A portion of the inner surfaces defining void <NUM> are not threaded to enable the bonnet <NUM> to outwardly bear against the body <NUM>. Void <NUM> accommodates the bonnet screw <NUM>, a portion of the bonnet <NUM>, at least a portion of the diaphragm plate <NUM>, a portion of the first spring <NUM>, and the diaphragm <NUM> when in the neutral or upwardly flexed positions. As shown in <FIG>, void <NUM> includes a ringed portion <NUM> which extends into the body <NUM> at a non-perpendicular angle with respect to the longitudinal axis L.

Void 13n is ring-shaped with a central axis collinear with the longitudinal axis L. Void 13n accommodates the o-ring <NUM>. As shown in <FIG>, the bottom of void 13n is uneven by virtue of an upwardly extending surface <NUM> configured to deform the o-ring <NUM>. Void 13p is ring-shaped, lies below void <NUM>, and has a central axis collinear with the longitudinal axis L. Void 13q has a central axis offset from, but parallel with the longitudinal axis L and connects port 13c with void <NUM> via void 13p.

With reference to <FIG>, the pin <NUM> includes an upper portion <NUM> and a lower portion <NUM>. The upper portion <NUM> includes a protruding portion 201a and a main portion 201b. The protruding portion 201a defines void 20c. Void 20c is partially conical and has a central axis collinear with the longitudinal axis L and fluidly communicates with void <NUM> via the first seat disc <NUM>. The protruding portion 201a includes the valve seat <NUM> for sealingly engaging the first seat disc <NUM>. The lower portion <NUM> includes an extension portion 202a, a guiding portion 202b, and an engaging portion 202c. The guiding portion 202b engages a top surface of the second seat disc <NUM> to longitudinally stabilize the second seat disc <NUM>. The engaging portion 202c extends into the second seat disc <NUM>.

As shown in <FIG>, the first seat disc <NUM> defines voids 17a, 17b, 17c, 17d, and 17e. Voids 17a and 17c are cylindrical and void 17c has a greater diameter than void 17a. Void 17b is channel-shaped and perpendicular to the longitudinal axis L. Void 17c is in fluid communication with void <NUM> of the body <NUM> via voids 17a and 17b. Void 17d is ring-shaped and extends from void 17c. Void 17e is conical. Voids 17a, 17b, 17c, 17d, and 17e respectively have central axes collinear with the longitudinal axis L.

The first seat disc <NUM> includes first and second upper surfaces <NUM> and <NUM>. The first upper surface <NUM> is circular and elevated above the second upper surface <NUM>. The first upper surface <NUM> bears against the diaphragm <NUM>. The second upper surface <NUM> defines a bottom of the channel-shaped void 17b disposed below the first upper surface <NUM> such that at least when the diaphragm <NUM> is in the neutral or flat position, the first upper surface <NUM>, but not the second upper surface <NUM>, bears on the diaphragm <NUM>. The first seat disc <NUM> includes an inner surface <NUM>, configured to compressively seal against pin <NUM>. As shown in <FIG>, the first seat disc <NUM> includes an outer perimeter <NUM> transitionally connected to the first upper surface <NUM> via rounded edges <NUM>. As shown in <FIG>, the outer perimeter <NUM> includes one or more outwardly extending sealing rings <NUM> to sealingly engage with the guide <NUM>.

<FIG> illustrates an alternative first seat disc <NUM> that may be substituted into the spindle <NUM> of <FIG> in place of the first seat disc <NUM>. As shown in <FIG>, the alternative first seat disc <NUM> defines voids 1700a, 1700b, 1700c, 1700d, and 1700e. Voids 1700a and 1700c are cylindrical and void 1700c has a greater diameter than void 1700a. Void 1700b is channel-shaped and perpendicular to the longitudinal axis L when the alternative first seat disc <NUM> is installed in the spindle <NUM>. Void 1700c is in fluid communication with void <NUM> of the body <NUM> via voids 1700a and 1700b when the alternative first seat disc <NUM> is installed in the spindle <NUM>. Void 1700d is toroidal and extends from void 1700c. Void 1700e is conical. Voids 1700a, 1700b, 1700c, 1700d, and 1700e respectively have central axes collinear with the longitudinal axis L.

The alternative first seat disc <NUM> includes first and second upper surfaces <NUM> and <NUM>. The first upper surface <NUM> is circular and elevated above the second upper surface <NUM>. The first upper surface <NUM> bears against the diaphragm <NUM>. The second upper surface <NUM> defines a bottom of the channel-shaped void 1700b disposed below the first upper surface <NUM> such that at least when the diaphragm <NUM> is in the neutral or flat position, the first upper surface <NUM>, but not the second upper surface <NUM>, bears on the diaphragm <NUM>. The alternative first seat disc <NUM> includes an inner surface <NUM>, configured to compressively seal against pin <NUM>. As shown in <FIG>, the first seat disc <NUM> includes an outer perimeter <NUM> transitionally connected to the first upper surface <NUM> via rounded edges <NUM>. As shown in <FIG>, the outer perimeter <NUM> includes an outwardly extending sealing ring <NUM> to sealingly engage with the guide <NUM>. The alternative first seat disc <NUM> includes a support ring <NUM> disposed in void 1700d. The support ring <NUM> provides outward support (e.g., radial stiffening) as the alternative first seat disc <NUM> sealingly engages with the guide <NUM> via the sealing ring <NUM>. In some examples, the support ring <NUM> is metallic (e.g., steel, stainless steel, brass, bronze, aluminum, etc.).

As shown in <FIG>, the guide <NUM> includes an upper surface <NUM>, outer threads <NUM>, an inner lip <NUM>, a bottom surface <NUM>, an unthreaded outer perimeter <NUM>, a rounded edge <NUM>, and an inner surface <NUM>. The guide <NUM> threadably engages with the body <NUM> via the outer threads <NUM>. The guide <NUM> defines voids 18a, 18b, 18c, and 18d. A tool may be inserted into voids 18b to tighten threaded engagement between the guide <NUM> and the body <NUM>. Void 18a has cylindrical and conical portions, has a central axis collinear with the longitudinal axis L, and is defined by the inner lip <NUM>. Void 18c is cylindrical with a diameter greater than the cylindrical portion of void 18a, has a central axis collinear with the longitudinal axis L. Void 18c is transitionally connected to the cylindrical portion of void 18a via the conical portion of void 18a. Void 18d is conical and transitionally connects the inner surface <NUM> to the bottom surface <NUM>. The unthreaded outer perimeter <NUM> is transitionally connected to the bottom surface <NUM> via the rounded edge <NUM>. The inner lip <NUM> has a diameter less than the inner surface <NUM>. The inner lip <NUM> bears against the outer perimeter <NUM> of the first seat disc <NUM> and captures the first seat disc <NUM> via the sealing rings <NUM>.

As shown in <FIG>, the seat screw <NUM> includes an upper surface <NUM>, outer threads <NUM>, a bottom surface <NUM>, at least one chamfer <NUM>, and an inner surface <NUM>. Voids 21a and 21b are defined by the inner surface <NUM>. Void 21a is cylindrical and has a central axis collinear with the longitudinal axis L. Each void 21b forms a corner in communication with void 21a. In other words, the voids 21b are extensions (e.g., offshoots) of cylindrical void 21a. The seat screw <NUM> is threadably engaged with the body <NUM> via the outer threads <NUM>. Void 21a accommodates the pin <NUM> to slidably engage the pin <NUM> with the inner surface <NUM> and each void 21b forms a fluid passage between the seat screw <NUM> and the pin <NUM>. In operation, fluid communicates between voids 22c and 18c (shown in <FIG>) via voids 21b. A tool may be inserted into voids 21b to tighten threaded engagement between the seat screw <NUM> and the body <NUM>. In other words, the voids 21b serve to convey fluid when the pin <NUM> is inserted into void 21a and to provide at least one tool engagement surface. In the illustrated example of <FIG>, the voids 21b are arranged hexagonally. It should be understood that the seat screw <NUM> may define any number of voids 21b greater than zero and that the voids 21b may be any shape (e.g., rectangular, lobed, etc.). Chamfer <NUM> provides a lead-in to facilitate insertion of the pin <NUM> into the seat screw <NUM> and sliding engagement of the pin <NUM> with the seat screw <NUM>.

With reference to <FIG>, the seat <NUM> defines voids 22a, 22b, 22c, and 22d. Voids 22a and 22b are cylindrical and have respective central axes collinear with the longitudinal axis L. Void 22a has a greater diameter than void 22b. Void 22d is conical and transitionally connects voids 22a and 22b. Voids 22a and 22b accommodate a portion of the pin <NUM>. Void 22c is channel-shaped, is substantially perpendicular with the longitudinal axis L, and links to void 13f. The seat <NUM> includes a first upper surface <NUM>, a first shoulder <NUM> for engaging the washer <NUM>, a second shoulder <NUM>, and a second upper surface <NUM>. The second upper surface <NUM> is disposed below the first upper surface to define the channel-shaped void 22c. The second shoulder <NUM> includes the ring-shaped valve seat <NUM> for bearing against the second seat disc <NUM>. The valve seat <NUM> narrows as it extends in the downward direction, such that the outer diameter of the valve seat <NUM> shrinks while the inner diameter of the valve seat <NUM> remains constant.

With reference to <FIG>, the washer <NUM> includes an upper surface <NUM>, a bottom surface <NUM>, and an outer perimeter <NUM>. The washer <NUM> defines void 23a. Void 23a is cylindrical, has a central axis collinear with the longitudinal axis L, and accommodates a portion of the pin <NUM>. The upper surface <NUM> engages the first shoulder <NUM> of the seat <NUM>. The bottom surface <NUM> engages the body <NUM>.

With reference to <FIG>, the second seat disc <NUM> defines voids 26a, 26b, 26c, 26d, and 26e. Voids 26a, 26b, 26c, 26d, and 26e respectively have central axes collinear with the longitudinal axis L. Void 26d is conical. Voids 26a, 26b, 26c, and 26e are cylindrical. Void 26a has a smaller diameter than void 26b. Void 26b receives the guiding portion 202b of the pin <NUM>. Void 26a receives the engaging portion 202c of the pin <NUM>. The second seat disc <NUM> includes a first upper surface <NUM> configured to compressively seal against the seat <NUM>, a shoulder <NUM> configured to receive and inwardly bear against the second spring <NUM>, and a first outer perimeter <NUM> including a flat surface <NUM> and a round portion <NUM>. The flat surface <NUM> provides clearance for the second seat disc <NUM> in void 13e. The second seat disc <NUM> also includes a second outer perimeter <NUM>, a transitional surface <NUM>, and a bottom surface <NUM>. The round portion <NUM> has a diameter greater than the second outer perimeter <NUM>. The transitional surface <NUM> is conical to transition between the second outer perimeter <NUM> and the first outer perimeter <NUM>. A rounded edge <NUM> is formed between the round portion <NUM> and the bottom surface <NUM>. A square edge <NUM> is formed between the flat surface <NUM> and the bottom surface <NUM>.

As shown in <FIG>, the bonnet <NUM> defines voids 7a, 7b, and 7c. Voids 7a, 7b, and 7c are cylindrical and have central axes collinear with longitudinal axis L. The diameter of void 7a is smaller than the diameter of void 7b. The diameter of void 7b is smaller than the diameter of void 7c. The bonnet <NUM> includes the first shoulder <NUM>, a second shoulder <NUM>, and a third shoulder <NUM>. The diaphragm <NUM> engages with the second shoulder <NUM>. The bonnet screw <NUM> engages with the third shoulder <NUM>. The bonnet <NUM> includes internal threads <NUM>, which define void 7a, and a vent hole <NUM>. Void 7c accommodates the diaphragm plate <NUM>. Void 7b accommodates the first spring <NUM> and the spring support <NUM>.

With reference to <FIG> and <FIG>, the bonnet screw <NUM> is ring-shaped and defines an inner cylindrical void 9a with a central axis collinear with the longitudinal axis L. The bonnet screw <NUM> defines a plurality of rectangular slots 9b. A tool may be inserted into the slots 9b to enable a user standing above the bonnet <NUM> to torque the bonnet screw <NUM>. Put differently, without slots 9b, a user would be unable to torque the bonnet screw <NUM> because outer walls of the body <NUM> surround the bonnet screw <NUM>. The bonnet screw <NUM> includes outer threads <NUM> configured to engage inner threads of the body <NUM>. The outer threads <NUM> may be continuous about an outer perimeter of the bonnet screw <NUM> or may be absent during intervals corresponding to slots 9b. The bonnet screw <NUM> further includes a bottom surface <NUM>. The bottom surface <NUM> engages with the third shoulder <NUM> of the bonnet <NUM>.

<FIG> show the diaphragm <NUM> prior to deformation and installation into the valve <NUM>. Prior to deformation, the diaphragm <NUM> is a flat, circular, and continuous piece of metal. After deformation, and when the diaphragm <NUM> is in the neutral or flat position, as shown in <FIG>, a circular inner portion is elevated above a ring-shaped outer portion. The circular inner portion is configured to contact the first seat disc <NUM> and the diaphragm plate <NUM>. The ring-shaped outer portion is configured to contact the o-ring <NUM>. Upon deformation, the diaphragm <NUM> remains continuous and solid to substantially prevent fluid from leaking into the interface between the diaphragm plate <NUM> and the bonnet <NUM>.

With reference to <FIG>, the o-ring <NUM> includes an outer perimeter <NUM> and defines void 14a. The o-ring <NUM> is substantially toroidal (e.g., doughnut-shaped). Void 14a has a central axis collinear with the longitudinal axis L. The o-ring <NUM> sealingly engages with the body <NUM> via void 13n and with the diaphragm <NUM>.

With reference to <FIG>, the spring support <NUM> includes an upper surface <NUM>, a bottom surface <NUM>, a shoulder <NUM>, a chamfer <NUM>, and an outer perimeter <NUM> and defines voids 6a and 6b. Voids 6a and 6b have central axes collinear with the longitudinal axis L. Void 6a is cylindrical and partially conical. Void 6b is conical. Voids 6a and 6b accommodate the ball <NUM>. The shoulder <NUM> transitions to the bottom surface via the chamfer <NUM>. The shoulder <NUM> engages with the first spring <NUM>. The shoulder <NUM> and the top surface <NUM> respectively transition to the outer perimeter <NUM> via rounded edges. The chamfer <NUM> may provide a lead-in to facilitate engaging the first spring <NUM> with the shoulder <NUM>.

As shown in <FIG>, the diaphragm plate <NUM> includes a lower surface <NUM>, a first upper surface <NUM>, a second upper surface <NUM>, a first ring <NUM>, and a second ring <NUM> and defines inner voids 10a and 10b. Inner void 10a is defined by the first ring <NUM>, is cylindrical, and has a central axis collinear with the longitudinal axis L. Inner void 10b is defined by the first ring <NUM> and the second ring <NUM>, has a central axis collinear with the longitudinal axis L, and is configured to receive the first spring <NUM>. By virtue of first spring <NUM>, the lower surface <NUM> engages with the diaphragm <NUM> substantially continuously (i.e., lower surface <NUM> contacts the diaphragm <NUM> in all of the neutral or flat, upwardly flexed, and downwardly flexed positions). The first lower surface <NUM> is disposed below to the second upper surface <NUM>. The first ring <NUM> has a smaller diameter than the second ring <NUM>. The spring <NUM> is thus captured between the first ring <NUM> and the second ring <NUM>. The first ring <NUM> is chamfered to facilitate insertion of the first spring <NUM> into void 10b. The second upper surface <NUM> is configured to contact shoulder or step <NUM> of bonnet <NUM> to arrest upward flexing of diaphragm <NUM>.

<FIG> illustrate exemplary structural features of an alternative combination regulator valve <NUM>. The alternative valve <NUM> is an alternative embodiment of the valve <NUM> of <FIG>. With reference to <FIG>, the alternative valve <NUM> has the longitudinal axis L and includes the setting portion <NUM> and its respective components of <FIG>, <FIG>, and <FIG> as described above joined with an alternative flowing portion <NUM>. The alternative valve <NUM> serves as a fluid economizer and as a fluid regulator. When serving as a fluid economizer, alternative valve <NUM> accepts fluid at a second port 131b and expels the fluid through a third port 131c. When serving as a fluid regulator, alternative valve <NUM> accepts fluid at a first port 131a and expels the fluid through the second port 131b.

The alternative flowing portion <NUM> is configured to (a) enable internal fluid communication between the first port 131a and the second port 131b, (b) enable internal fluid communication between the second port 131b and the third port 131c, and (c) disable internal fluid communication between the first, second and third ports 131a, 131b, 131c. With reference to <FIG>, the alternative flowing portion <NUM> includes an alternative body <NUM>, the o-ring <NUM> of <FIG> and <FIG>, the spindle unit <NUM> and its respective components of <FIG> and <NUM>-<NUM>, and the diaphragm <NUM> of <FIG> and <FIG>.

With reference to <FIG>, the bonnet screw <NUM> compresses the bonnet <NUM> against the first and second outer portions of the diaphragm <NUM>. The first outer portion of the diaphragm <NUM> is compressed between the o-ring <NUM> and the bonnet <NUM>. The second outer portion is radially outward of the first outer portion and is compressed between the alternative body <NUM> and the bonnet <NUM>. Thus, the diaphragm <NUM> discourages fluid leakage from void <NUM> and past the bonnet <NUM> at the first outer portion and at the second outer portion.

The guide <NUM> is threaded into the alternative body <NUM>. The seat screw <NUM> is threaded into the alternative body <NUM> and axially bears on the seat <NUM> to capture the seat <NUM> in the alternative body <NUM>. The washer <NUM> is compressed between the seat <NUM> and the alternative body <NUM> to discourage fluid from flowing between the alternative body <NUM> and the seat <NUM>. The second seat disc <NUM> receives the second spring <NUM> to capture the second spring <NUM> between the second seat disc <NUM> and the alternative body <NUM> and to longitudinally align the second spring <NUM> with the longitudinal axis L. Further connections and interactions of the components of the spindle unit <NUM> are as described above.

As described above, the first spring <NUM> biases the diaphragm <NUM> downward. Fluid pressure in void <NUM> biases the diaphragm <NUM> upward. Additionally, fluid pressure in voids of the spindle unit <NUM> bias diaphragm <NUM> upward as described above. Similarly, fluid pressure in void 131e biases diaphragm <NUM> upward, but only until upward movement of the spindle unit <NUM> is stopped as described above.

These biases and fluid pressures apply force to the diaphragm <NUM> and thus determine whether the diaphragm <NUM> is upwardly flexed, downwardly flexed, or neutral. It should be appreciated that because void <NUM> has a greater area parallel to diaphragm <NUM> than the voids of the spindle unit <NUM>, pressure in void <NUM> influences the position of diaphragm <NUM> to a greater extent than pressure in the spindle unit <NUM>.

Upon installation, a user cannot access the spindle unit <NUM> or the diaphragm <NUM> without removing the bonnet <NUM>. Thus, by rotating the screw <NUM>, the user may control the fluid pressures in void <NUM> and in the spindle unit <NUM> that causes diaphragm <NUM> to flex upwardly and downwardly as described above with respect to voids <NUM> and 17c.

When the diaphragm <NUM> downwardly flexes, the spindle unit <NUM> is displaced to permit fluid communication between the first port 131a and the second port 131b via voids 131d, 131e, the spindle unit <NUM>, and void 131f. When the spindle unit <NUM> is displaced downwardly, internal fluid communication is blocked between (a) the first and second ports 131a, 131b and (b) the third port 131c through the alternative flowing portion <NUM>. Put differently, internal fluid communication only occurs between the first and second ports 131a and 131b.

When fluid pressure in void <NUM> flexes the diaphragm <NUM> upward past the neutral or flat position, the spindle unit <NUM> occupies the closed position shown in <FIG> similar to the closed position of <FIG>.

Fluid pressure in void <NUM> spread across the surface area of the diaphragm <NUM> produces a first force. Fluid pressure in void <NUM> spread across the surface area of the topside of the first seat disc of the spindle unit <NUM> produces a second force, as described above. Fluid pressure in the spindle unit <NUM> produces a third force, as described above. When the first force overcomes the downward force of the setting portion <NUM>, the diaphragm <NUM> flexes upwardly. When the third force overcomes the second force, the first seat disc disengages from the pin of the spindle unit <NUM> as described above. Similar to above, a first minimum fluid pressure in void <NUM> spread across the surface area of the diaphragm <NUM> overcomes the downward force of the setting portion <NUM> and a second minimum pressure in the spindle unit <NUM> spread across the a portion of the bottom surface area of the first seat disc overcomes the downward force of fluid pressure in void <NUM> spread across the top surface area of the spindle unit <NUM>. Thus, fluid communication is enabled between the second port 131b and the third port 131c via voids 131f, and 131q and the spindle unit <NUM>.

Similar to above, when the diaphragm <NUM> flexes upwardly, internal fluid communication is blocked between (a) the first port 131a and (b) the second and third ports 131b, 131c. Put differently, internal fluid communication only occurs between the second and third ports 131b, 131c.

When the diaphragm <NUM> is in the neutral or flat position, as shown in <FIG>, the diaphragm <NUM> counters the upward force of fluid pressure in the spindle unit <NUM> and the spindle unit <NUM> occupies the closed position, as described above. As a result, the alternative valve <NUM> blocks internal fluid communication between all of the first, second, and third ports 131a, 131b, 131c.

As shown in <FIG>, the alternative body <NUM> defines (a) first, second, and third ports 131a, 131b, 131c and (b) voids 131d, 131e, 131f, <NUM>, <NUM>, 131i, 131j, <NUM>, <NUM>, 131n, 131p, and 131q. For the reader's convenience and to avoid confusion, the void numbering skips <NUM> and 131o.

The first, second, and third ports 131a, 131b, 131c are partially conical and transversely extending in the body <NUM>. The second and third ports 131b, 131c are opposite one another with collinear central axes. The first port 131a has a central axis perpendicular to the central axes of the second and third ports 131b, 131c.

Void 131d is cylindrical with a central axis angled with respect to the longitudinal axis L and the central axis of the first port 131a. Void 131e is cylindrical and linked to void 131a via void 131d. Void 131e has a central axis parallel to and collinear with the longitudinal axis L. Void 131e accommodates the spindle unit <NUM> in the same manner as void 13e, described above. Void 131f, has a central axis perpendicular to the longitudinal axis L, has three lobes, and links the second port 131b with voids of the spindle unit <NUM> in the same manner as void 13f, described above.

Void <NUM> is disc shaped and accommodates the spindle unit <NUM> in the same manner as void <NUM>, described above. A central axis of void <NUM> is collinear with the longitudinal axis L. Void <NUM> has a maximum diameter exceeding the maximum diameters of voids 131e and <NUM>.

Void <NUM> is cylindrical. Inner surfaces of the alternative body <NUM> defining void <NUM> are threaded to threadably engage with the spindle unit <NUM>. A central axis of void <NUM> is parallel to the longitudinal axis L. Void <NUM> accommodates the spindle unit <NUM> in the same manner as void <NUM>, described above. Void 131i is a conical transition between voids <NUM> and 131j. Void 131i has a larger major diameter than the non-threaded portion of void <NUM> and a central axis collinear with longitudinal axis L.

Void 131j is cylindrical. Inner surfaces of the alternative body <NUM> defining void 131j are threaded to threadably engage with the spindle unit <NUM>. A central axis of void 131j is parallel to the longitudinal axis L. Void 131j accommodates the spindle unit <NUM> in the same manner as void 13j, described above. Void <NUM> is cylindrical with a central axis collinear with the longitudinal axis L. Void <NUM> has a greater diameter than any of voids 131e, <NUM>, <NUM>, 131i, and 131j. Void <NUM> accommodates the spindle unit <NUM> in the same manner as void <NUM>, described above. When downwardly flexed, the diaphragm <NUM> protrudes into void <NUM>.

Void <NUM> is cylindrical with a central axis collinear with the longitudinal axis L. A portion of the inner surfaces of the alternative body <NUM> defining void <NUM> are threaded to threadably engage with the bonnet screw <NUM>. A portion of the inner surfaces defining void <NUM> are not threaded to enable the bonnet <NUM> to outwardly bear against the alternative body <NUM>. Void <NUM> accommodates the diaphragm <NUM> when in the neutral or upwardly flexed positions and the spindle unit <NUM> in the same manner as void <NUM>, described above.

Void 131n is ring-shaped with a central axis collinear with the longitudinal axis L. Void 131n accommodates the o-ring <NUM>. Void 131p is ring-shaped, lies below void <NUM>, and has a central axis collinear with the longitudinal axis L. Void 131q has a central axis offset from, but parallel with the longitudinal axis L and connects the third port 131c with void <NUM> via void 131p.

Several advantages are offered by the valve and the alternative valve. First, the valve <NUM> and the alternative valve <NUM> separate the regulator function from the economizer function by applying two different independently moveable seat discs <NUM>, <NUM>. The inclusion of independently moveable seat discs reduces the chances of unintended fluid communication between all three ports 13a, 13b, 13c in the valve <NUM> or between all three ports 131a, 131b, 131c when only fluid communication between two of the ports is desired.

Second, bonnet <NUM> and body <NUM> confine spindle unit <NUM> within valve <NUM> and within the alternative valve <NUM>. This confinement reduces the possibility of external leakage through the valve <NUM> or through the alternative valve <NUM> and reduces the chances of damage to spindle unit <NUM>.

Third, by applying the bonnet screw <NUM> to lock the bonnet <NUM> with respect to the body <NUM> or to the alternative body <NUM>, the chances of damage to the diaphragm <NUM> are reduced. Put differently, the bonnet screw <NUM> enables a user to stably and reliably compress diaphragm <NUM> between the bonnet <NUM> and the body <NUM> or the alternative body <NUM>. In at least some prior art designs, a bonnet is directly threaded to a body, which increases the chances of damaging a diaphragm, compressed between the bonnet and the body, during assembly. This is because the absence of a bonnet screw prevents a user from reliably controlling the compression between the body and the bonnet.

Fourth, the valve <NUM> and the alternative valve <NUM> enable a user to replace internal components in a single direction. More specifically, after disengaging the bonnet screw <NUM> and removing the bonnet <NUM>, a user can access and remove all of the spindle unit <NUM> when looking down at the body <NUM> or the body <NUM>.

Fifth, the valve <NUM> and the alternative valve <NUM> generate a metal-to-metal seal between diaphragm <NUM> and the body <NUM> or the alternative body <NUM>, respectively, along the outer circumference of the diaphragm <NUM>. The bonnet <NUM> compresses the diaphragm <NUM> against the body <NUM> or the alternative body <NUM> to ensure the integrity of the seal. Besides generating a tight seal, this compression ensures that the diaphragm <NUM> does not move horizontally or laterally (i.e., perpendicular to longitudinal axis L) during operation.

Sixth, the o-ring <NUM> provides an additional seal that discourages fluid from leaking past the diaphragm <NUM> and between the bonnet <NUM> and the body <NUM> or the alternative body <NUM>. Additionally, the o-ring <NUM>, by acting as a spring, absorbs some downward force applied to the diaphragm <NUM>. As a result, the o-ring <NUM> reduces the chances that downward force generated by the bonnet screw <NUM> and applied by the bonnet <NUM> will crack the diaphragm <NUM>. Furthermore, the presence of the o-ring <NUM> enables the diaphragm <NUM> to flex to a greater extent than at least some prior art diaphragms. More specifically, because the o-ring <NUM> acts as a spring to absorb forces applied against the diaphragm <NUM>, the diaphragm <NUM> can tolerate the greater forces associated with more extreme flexing positions.

Seventh, because the seat <NUM> is separate from body <NUM> and from the alternative body <NUM>, a user can machine the sealing surface (valve seat <NUM>) against which second seat disc <NUM> seals prior to assembly. In at least some prior art designs, valve seats are formed on inner surfaces of a body. As a result, it is difficult to access and thus accurately machine these prior art valve seats. When those inner surfaces are downwardly facing, a bottom portion of the body may be threadably detachable from a top portion of the body to enable tool access to the downwardly facing inner surfaces. Because the seat <NUM> is removable, the body <NUM> and the alternative body <NUM> can be integrally formed. Additionally, a user may periodically replace the seat <NUM> without replacing the body <NUM> or the alternative body <NUM>. When valve seats are formed on inner surfaces of a body, these valve seats cannot be replaced without replacing the entire body.

Eighth, the first seat disc <NUM> is confined between the diaphragm <NUM> and the pin <NUM>. As a result, the first seat disc <NUM> does not need to be attached to the diaphragm <NUM>. In at least some prior art designs, a seat disc is attached to a diaphragm, necessitating a hole in the diaphragm for receiving the seat disc. Consequently, the present disclosure enables the diaphragm <NUM> to be a solid piece of material, which reduces the chances of leakage through the diaphragm <NUM>.

Ninth, the first seat disc <NUM> is an upside-down bowl design (i.e., bowl-shaped), which discourages contaminants from resting between the pin <NUM> and the inner surface <NUM> of the first seat disc <NUM>. Furthermore, the top of the first seat disc <NUM> includes an upper surface <NUM> and a lower surface <NUM>. Contaminants resting between the diaphragm <NUM> and the first seat disc <NUM> will thus be biased from the upper surface <NUM> toward the lower surface <NUM> due to the contact between the upper surface <NUM> and the diaphragm <NUM>.

This list of advantages is not exhaustive. Additional advantages of the invention are apparent with reference to other sections of the specification and the figures.

The o-rings <NUM> and the washer <NUM> may be a compressible polymer such as PTFE or Omni-seal. The diaphragm <NUM>, the body <NUM>, and the alternative body <NUM> may be metals. The first and second seat discs <NUM>, <NUM> may be a compressible material such as PTFE to discourage the first seat disc <NUM> from damaging the diaphragm <NUM> and to discourage the second seat disc <NUM> from damaging the seat <NUM>. The remaining components of the valve <NUM> and the alternative valve <NUM> may be metal.

<FIG> schematically illustrates a cryogenic system <NUM> for receiving, storing, and dispensing cryogenic fluid (e.g., natural gas, oxygen, etc.). Cryogenic system <NUM> includes the valve <NUM>, a tank <NUM> (which includes an inner tank <NUM> and an outer tank <NUM>), liquid phase fluid <NUM>, gas phase fluid <NUM>, a first two-way valve <NUM>, a second two-way valve <NUM>, a four-way junction or valve <NUM>, a two-way vent valve <NUM>, an inner tank rupture disk <NUM>, a pressure gauge <NUM>, a safety relief valve <NUM>, an outer tank rupture disc <NUM>, lines <NUM> to <NUM>, and a three-way junction <NUM>. It should be understood that, in another embodiment, the alternative valve <NUM> may also be used in the cryogenic system <NUM> in place of the valve <NUM>.

The tank <NUM> includes a protective outer tank <NUM> and an inner tank <NUM> for storing the fluid. Fluid inside the inner tank <NUM> naturally separates into liquid fluid <NUM> and a gas fluid <NUM>. Lines <NUM> and <NUM> fluidly communicate at the three-way junction <NUM>. Although lines <NUM> and <NUM> cross, lines <NUM> and <NUM> are distinct and not in fluid communication, as indicated by the jumpover in <FIG>. Line <NUM> extends to a lower portion of the tank <NUM> to communicate with liquid fluid <NUM>. Line <NUM> extends to an upper portion of the tank <NUM> to communicate with gas fluid <NUM>. Line <NUM> is a pressure building coil and accepts liquid fluid <NUM> from a bottom of the tank <NUM>. Line <NUM> is a vaporizer. Line <NUM> connects to the first port 13a. Line <NUM> connects to the second port 13b. Line <NUM> connects to the third port 13c. Junction or four-way valve <NUM> is configured to fluidly communicate lines <NUM>, <NUM>, <NUM>, and <NUM>. Junction or four-way valve <NUM> may enable a user to selectively isolate some or all of lines <NUM>, <NUM>, <NUM>, and <NUM> from junction or four-way valve <NUM>.

A user may fill the tank <NUM> by connecting a source of cryogenic fluid to line <NUM> and opening the first two-way valve <NUM>. A user may withdraw liquid fluid through line <NUM> after opening the first two-way valve <NUM>. A user may withdraw gas fluid through line <NUM> after opening the second two-way valve <NUM>.

As described above, the valve <NUM> is configured to (a) enable internal fluid communication between the first port 13a and the second port 13b, (b) enable internal fluid communication between the second port 13b and the third port 13c, and (c) disable internal fluid communication between the first, second, and third ports 13a, 13b, and 13c. As described above, the valve <NUM> is configured to perform these functions based on fluid pressure in voids <NUM>, 17c, and 13e. Fluid from the tank <NUM> enters void <NUM> via line <NUM>, the four-way valve <NUM>, line <NUM>, and the third port 13c. Fluid from the tank <NUM> enters void 17c via line <NUM> and the second port 13b. Fluid from the tank <NUM> enters void 13e via line <NUM> and the first port 13a.

The valve <NUM> is configured to enable internal fluid communication between the first port 13a and the second port 13b when pressure of fluid in the tank <NUM> is below a first predetermined pressure. Due to the low pressure, and as previously discussed, the diaphragm <NUM> occupies the downwardly flexed position. As a result, the second seat disc <NUM> is disengaged from the seat <NUM>, and the first seat disc <NUM> is engaged with the pin <NUM>. Therefore, fluid communication through the valve <NUM> between the first port 13a and the second port 13b is enabled while fluid communication through the valve <NUM> between (a) the first and second ports 13a and 13b and (b) the third port 13c is disabled. When fluid communication between the first and second ports 13a and 13b is enabled, liquid fluid enters line <NUM> (the pressure building coil), which vaporizes the liquid fluid into a gas fluid. The gas fluid enters the first port 13a, flows through the second port 13b, and reenters the tank <NUM> as a gas. As a result, pressure in the tank <NUM> increases.

The valve <NUM> is configured to enable internal fluid communication between the second port 13b and the third port 13c when pressure in the tank <NUM> is above a second predetermined pressure. The second predetermined pressure is greater than the first predetermined pressure. Due to the higher pressure, as previously discussed, the diaphragm <NUM> occupies the upwardly flexed position. As a result, the second seat disc <NUM> is engaged with the seat <NUM>. When a user opens the first two-way valve <NUM> and/or the second two-way valve <NUM>, which are in fluid communication with the third port 13c, fluid pressure in void <NUM> decreases suddenly while fluid pressure in void 17c substantially remains at the higher pressure. Thus, a pressure differential is formed between voids <NUM> and 17c. Due to the pressure differential, the first seat disc <NUM> is disengaged from pin <NUM>. Therefore, fluid communication through the valve <NUM> between the second port 13b and the third port 13c is enabled while fluid communication through the valve <NUM> between (a) the second and third ports 13b and 13c and (b) the first port 13a is disabled.

When fluid communication between the second and third ports 13b and 13c is enabled and a user has opened two-way valve <NUM>, fluid flows from line <NUM>, through valve <NUM>, into line <NUM>, through the junction or four-way valve <NUM>, through line <NUM>, and into the vaporizer <NUM>. The vaporizer <NUM> converts any remaining liquid fluid into gas fluid and delivers the gas fluid to the two-way valve <NUM>. Fluid is dispensed to a consumer (e.g., an engine) via line <NUM>.

Claim 1:
A valve (<NUM>, <NUM>) for conveying fluid, the valve (<NUM>, <NUM>) comprising:
a body (<NUM>, <NUM>) that is integrally formed and defines a plurality of ports (13a, 13b, 13c, 131a, 131b, 131c), and defining a plurality of voids (13d, 13e, 13f, <NUM>, <NUM>, 13i, 13j, <NUM>, <NUM>, 13n, 13p, 13q, 131d, 131e, 131f, <NUM>, <NUM>, 131i, 131j, <NUM>, <NUM>, 131n, 131p, 131q), wherein the plurality of voids (13d, 13e, 13f, <NUM>, <NUM>, 13i, 13j, <NUM>, <NUM>, 13n, 13p, 13q, 131d, 131e, 131f, <NUM>, <NUM>, 131i, 131j, <NUM>, <NUM>, 131n, 131p, 131q) include cylindrical voids (13e, <NUM>, <NUM>, 13j, <NUM>, <NUM>, 131e, <NUM>, <NUM>, 131j, <NUM>, <NUM>) that have a central axis parallel to and collinear with a longitudinal axis of the body (<NUM>, <NUM>);
a bonnet (<NUM>) secured to the body (<NUM>, <NUM>) and defining a bonnet void;
a diaphragm (<NUM>) compressed between the bonnet (<NUM>) and the body (<NUM>, <NUM>);
a first spring (<NUM>) disposed in the bonnet void and configured to bias the diaphragm (<NUM>) in a downward direction; and
a spindle unit (<NUM>) confined in the plurality of voids (13d, 13e, 13f, <NUM>, <NUM>, 13i, 13j, <NUM>, <NUM>, 13n, 13p, 13q, 131d, 131e, 131f, <NUM>, <NUM>, 131i, 131j, <NUM>, <NUM>, 131n, 131p, 131q) of the body (<NUM>, <NUM>), wherein the spindle unit (<NUM>) comprises:
a second spring (<NUM>) configured to bias the spindle unit (<NUM>) upwardly;
a pin (<NUM>) and a first seat disc (<NUM>), wherein the first seat disc (<NUM>) is configured to contact the pin (<NUM>), and wherein the plurality of ports (13a, 13b, 13c, 131a, 131b, 131c) comprise a first port (13a, 131a), a second port (13b, 131b), and a third port (13c, 131c);
a second seat disc (<NUM>) and a seat (<NUM>), wherein the pin (<NUM>) is inserted into the second seat disc (<NUM>), wherein the second spring (<NUM>) is received by the second seat disc (<NUM>) to capture the second spring (<NUM>) between the second seat disc (<NUM>) and the body (<NUM>, <NUM>);
a guide (<NUM>) threaded into the body (<NUM>, <NUM>) and bearing on the first seat disc (<NUM>) to longitudinally align the first seat disc (<NUM>) along the longitudinal axis of the body (<NUM>, <NUM>); and
a seat screw (<NUM>) threaded into the body (<NUM>, <NUM>) and inwardly bearing on the pin (<NUM>), wherein the seat screw (<NUM>) and the pin (<NUM>) define a fluid passage in fluid communication with the second port (13b, 131b).