US20040007269A1 - Inline pressure reducing regulator - Google Patents

Inline pressure reducing regulator Download PDF

Info

Publication number
US20040007269A1
US20040007269A1 US10194717 US19471702A US2004007269A1 US 20040007269 A1 US20040007269 A1 US 20040007269A1 US 10194717 US10194717 US 10194717 US 19471702 A US19471702 A US 19471702A US 2004007269 A1 US2004007269 A1 US 2004007269A1
Authority
US
Grant status
Application
Patent type
Prior art keywords
piston
portion
body
bore
bonnet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10194717
Inventor
Todd Larsen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tescom Corp
Original Assignee
Tescom Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date

Links

Images

Classifications

    • GPHYSICS
    • G05CONTROLLING; REGULATING
    • G05DSYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00Control of fluid pressure
    • G05D16/04Control of fluid pressure without auxiliary power
    • G05D16/10Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
    • G05D16/103Control of fluid pressure without auxiliary power the sensing element being a piston or plunger with sensing element placed within the flow-path
    • G05D16/106Control of fluid pressure without auxiliary power the sensing element being a piston or plunger with sensing element placed within the flow-path using sliding elements
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/7722Line condition change responsive valves
    • Y10T137/7781With separate connected fluid reactor surface
    • Y10T137/7793With opening bias [e.g., pressure regulator]
    • Y10T137/7808Apertured reactor surface surrounds flow line
    • YGENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/7722Line condition change responsive valves
    • Y10T137/7781With separate connected fluid reactor surface
    • Y10T137/7834Valve seat or external sleeve moves to open valve

Abstract

The pressure reducing regulator includes a regulator body with a tubular portion coaxially aligned with the tubular portion of a bonnet threaded to the regulator body. A piston has a bore extending therethrough with the tubular portions extended thereinto in axial spaced relationship, the body tubular portion mounting a valve seat to abut against a piston internal shoulder when the piston has axially moved relative to the tubular portions to a blocking position to block fluid flow through the regulator. The piston enlarged diametric portion bottom surface is in fluid communication with the piston bore in both of the piston positions but not in fluid communication with the body high pressure inlet when the piston is in its blocking position. A spring resiliently retains the piston in its open position when no pressurized fluid is applied to the body inlet.

Description

    BACKGROUND OF THE INVENTION
  • This invention is for a pressure regulator that is mountable in a line between a source of pressurized fluid and an object to which a fluid under a lower controlled pressure is to be applied. [0001]
  • In Gold, U.S. Pat. No. 4,667,695, there is disclosed an annular piston axially movable in a bore in a body (second piston). The annular piston is resiliently urged to a position to permit fluid flow therethrough from its inlet end to its opposite end and thence through holes in the body. With an increase of pressure at the inlet end of the annular piston, the annular piston is moved toward its closed position. [0002]
  • Lachmann et al, U.S. Pat. No. 4,475,888, has a valve body with lower passages converging to open to a central bore while Miller, U.S. Pat. No. 5,501,247, discloses using a ke to prevent relative rotation between two parts of a pressure regulator. [0003]
  • In order to make improvements in inline pressure reducing regulators, this invention has been made. [0004]
  • SUMMARY OF THE INVENTION
  • The inline pressure reducing regulator includes a regulator body having an inlet that opens through a tubular portion (sleeve) that extends within a piston chamber to a piston bore portion and a bonnet having an outlet that opens through a bonnet tubular portion (sleeve) and apertures opposite the outlet to the piston bore. The piston has the body tubular portion extending into one end portion of the piston bore and the bonnet tubular portion extending into the other end of the piston bore. A valve seat is mounted by the apertured end of the bonnet sleeve to abut against an annular shoulder in the bore of the piston to block fluid flow therethrough. A first spring abuts against the body to urge the piston to a regulator closed position while a second spring abuts against the bonnet to urge the piston to a regulator open position. A key acts between the bonnet and regulator body to retain them in limited adjusted axial positions to permit a limited adjustment of the outlet pressure. [0005]
  • One of the objects of this invention is to provide a pressure reducing regulator having new and novel means for reducing the leakage paths between the regulator inlet and outlet. Another object of this invention to provide in a pressure regulator new and novel means for blocking fluid flow therethrough and if there is seat leakage, the extra outlet pressure increases the seat load to block fluid flow and form a new seat area to eliminate future leakage. An additional object of this invention is to provide in an inline pressure regulator, new and novel seat means for eliminating decaying inlet effects without the sacrifice of fluid flow shutoff. [0006]
  • Still another object of this invention is to provide new and novel means in an inline pressure regulator to minimize the possible leakage paths between the regulator inlet and the regulator outlet. A different object of this invention is to provide new and novel means in a pressure regulator for making small adjustments in the regulator outlet pressure. [0007]
  • Even though for convenience terms such as “upper”, “lower”, “top” and “bottom” will be used in describing the pressure regulator, it is to be understood the usage of these terms is applicable to when the pressure regulator is in an upright position such as illustrated. However, it is to be further understood that the pressure regulator may be used in other than an upright position.[0008]
  • BRIEF DESCRIPTION OF THE DRAWINGS
  • FIG. 1 is a cross sectional view of the first embodiment of the pressure regulator apparatus of this invention in its piston closed position for blocking fluid flow therethrough; [0009]
  • FIG. 2 is an enlarged fragmentary view of a portion of the structure of FIG. 1; [0010]
  • FIG. 3 is a still further enlarged view of the valve seat area of the regulator; and [0011]
  • FIG. 4 is a cross sectional view of the second embodiment of the invention. [0012]
  • DESCRIPTION OF THE PREFEERED EMBODIMENTS
  • Referring to FIG. 1 of the drawings, the inline pressure regulator apparatus of the first embodiment of the invention, generally designated [0013] 11, includes a regulator body, generally designated 10, with a bore B of varying diameters extending axially therethrough. A bonnet (cap), generally designated 12, is threadedly mounted to the upper portion of the body to close the upper end of the body bore. The bonnet has a bore D extending axially therethrough, other than for a valve seat 16 and the valve seat mount 24A, and is coaxial with the body bore.
  • The body bore B includes an axially intermediate bore portion [0014] 14 that is in part defined by an annular bottom wall 15 with an axially elongated sleeve (tubular portion) 17 integrally joined to the body lower part and extending axially a smaller distance above the bottom wall 15 than the axial dimension of the bore portion 14. The sleeve has a bore portion 18 extending axially therethrough and opens to the body pressurized body inlet 19 in the body part 17A, the bore portion 18 and inlet being parts of the body bore B. Thus, the sleeve opens to the intermediate bore portion axially intermediate its axially opposite ends. The bore portion 18 is of a much smaller diameter than that of each of the body intermediate bore portion and the inlet.
  • The body bore B also includes an enlarged diameter bore portion [0015] 20 that at its juncture with the axially intermediate bore portion forms an annular shoulder 21 and opens through the top annular edge of the regulator body to the annular top part 22 of the bonnet 12. The bore portion 20 is of a constant diameter for at least substantially the entire distance above the shoulder 21.
  • The bonnet has an annular portion [0016] 23 extending downwardly from the top part 22, the lower part of the annular portion being threadedly mounted to the regulator body. The bonnet also has an axially elongated tubular portion (sleeve) 24 integrally joined to and extending downwardly from the top part in coaxial relationship to the body sleeve, and advantageously is of a greater axial length than the bonnet annular portion 23. Thus the bonnet top part 27 has a wall that in part defines an annular chamber opening to the body enlarged bore portion and has the upper annular part 29 of the regulator body extended thereinto.
  • The bonnet tubular portion has a top part [0017] 24B that is of a given outer diameter for the major part of its length from the bonnet top part and has a reduced outer diameter part 24C to, at its juncture to the top part 24B, forms a downwardly facing shoulder 25. The reduced diameter part 24C at its lower end has the valve seat mount 24A formed integrally therewith. The seat mount at its upper end is of the same outer diameter as that of the tubular part 24C with the major base of a lower frustoconical portion 24E joined thereto. The frustoconical portion has its minor base joined to a cylindrical portion 24D. The reduced diameter part of the valve seat is extended into a socket in the cylindrical portion, the lower part of the seat being of a frustoconical shape for purpose that will be referred to hereinafter. The valve seat may be press fitted or otherwise suitably adhered to the seat mount without there being any threaded connection. The valve seat, in constantly being subjected to the high fluid pressure in the piston bore portion 38, acts to more firmly retain the valve seat mounted to the bonnet seat mount. As a result of the valve seat being mounted without the use of threads, there is a decreased chance of particle generation during assembly which could result in leakage flow bypassing the valve seat.
  • Mounted in the body bore portions [0018] 14, 20 for axial movement is annular piston (sensor) P, the piston having an enlarged diameter portion 30 to form a close sliding fit with the body wall portion that defines the cylindrical part of bore portion 20. The enlarged diametric portion has an annular groove with an O-ring 31 to form a fluid seal with the bore portion wall during the entire axial movement of the piston relative to the bonnet tubular portion. Further, the piston has an axial intermediate portion 32 joined to the enlarged diameter portion to extend downwardly thereof in bore portion 14 and is of a significantly smaller diameter than bore portion 14. The piston also includes a reduced diameter portion 33 joined to the intermediate portion 32 to extend downwardly thereof to provide a shoulder against which a coil spring 35 abuts. The opposite end of the spring abuts against the bottom wall 15 to constantly resiliently urge the piston axially away from the bottom wall 15. The movement of the piston in the opposite axial direction is limited by the piston enlarged diametric portion 30 abutting against the shoulder 21.
  • The piston has a top bore portion [0019] 37 opening through the top surface thereof and has the bonnet tubular portion 24C extended thereinto. The piston enlarged diametric portion has an internal groove with an O-ring 41 therein to provide a fluid seal with the tubular portion 24C as the piston moves axially relative to the tubular portion 24C. The axial movement of the piston axially away from the bottom wall 25 is limited by abutting against the shoulder 25.
  • The piston bore includes a lower bore portion [0020] 38 of a smaller diameter than that of bore portion 37 to provide an annular upwardly facing shoulder 39, the diameter of bore portion 38 being greater than the minimum diameter of the minor base of the frustoconical part 16A of the valve seat, but less than the maximum diameter of the major base of the frustoconical part 16A. The wall of the piston that defines bore portion 38 is of a diameter to form a close axial sliding fit with the body tubular portion 17, the piston reduced diameter portion 38 having an internal groove in which an O-ring 40 is mounted to form an axial fluid sealing fit with the tubular portion 17 during the entire axial movement of the piston relative to the tubular portion.
  • The frustoconical part [0021] 24E has a plurality of apertures 43 that converge upwardly to open to the bore 44 of the bonnet tubular portions 24B, 24C which in turn opens to regulator outlet (passage) 45 in the bonnet top portion 22. The apertures open to the annular clearance space 49 that is, at least in a substantial part, bounded by shoulder 39, the wall of the piston that defines the lower part of the tubular bore portion 37, the seat mount and the valve seat when the piston is in its closed (fluid flow blocking) position. When the piston is in its closed position, it has an axial intermediate part of the seat frustoconical portion 16A abutting against the piston at the juncture of the piston bore portions 37, 38 to block fluid flow from tubular portion bore 17 to the piston bore portion 37. Radial cross bores 48 are provided in the piston axial intermediate portion 32 to open to the clearance space 49 and to the annular clearance space 47 between the piston wall defining bore portion 14 and the part of the piston that extends below the piston enlarged diametric portion. The transverse area of the clearance space 47 is greater than that of the piston shoulder 39 such that even if the part of the bottom surface of the piston enlarged diametric portion were to abut against shoulder 21 and the part of the bottom surface piston of the piston reduced diameter portion were to abut against the body bottom wall 15, the part of the piston bottom surface subjected to pressurized fluid is sufficiently great to move the piston toward its closed position against the action of a coil spring 50 when the fluid pressure in the annular space 47 is at or above the preselected outlet pressure.
  • The coil spring [0022] 35 constantly resiliently urges the piston to a position that the part of the piston surrounding the opening of bore portion 38 to bore portion 37 abuts against the frustoconical part of valve seat to block high pressure fluid flow through the piston bore. The coil spring 50 is in the bore portion 20 and acts between the bonnet top portion 27 and the top surface of the piston to resiliently urge the piston to move relative to the bonnet tubular portion 24 to a regulator open position to permit high pressure fluid flow through the regulator. The spring 50 will retain the piston in an open position to place the bonnet tubular portion in fluid communication with the cross bores 50 and thereby with the annular clearance space 47 when no fluid under pressure is applied at the body inlet 19.
  • A stop screw [0023] 54 is threaded into the bonnet and extended into a regulator body annular groove 55 that is of a sufficient axial dimension to permit unthreading of the screw and then rotating the bonnet relative to the regulator body and thence threading the screw to abut against the regulator body for retaining the bonnet relative to the regulator body in an adjusted threaded (angular) position. Since such a threading adjustment varies the axial distance between the bonnet top portion 27 and the body shoulder 21, this provides small outlet pressure adjustments without the use of shims that are commonly used in conventional inline regulators. The annular groove is provided above the threaded connection between the regulator body upper portion 29 and the bonnet portion 23 while an O-ring 56 provides a fluid seal between the body portion 29 and bonnet portion 23 above the annular groove.
  • The bonnet has a vent port [0024] 52 that opens to the cavity (chamber) 34 between the tubular portion 24 and the body portion 29 axially between the top portion 27 and the piston. The leakage fluid in the above mentioned chamber can flow through the port 52 to a suitable container 53 for leakage gas or otherwise plumbed to a safe area. With the above bonnet-piston-regulator-O-ring arrangement, any and all leakage flow bypassing the O-rings flows through the port 52. Further, with this arrangement, the number of possible leakage paths between the inlet and outlet are reduced.
  • The outlet pressure can be adjusted by using springs [0025] 35 and 50 having the desired spring characteristics and the appropriate threaded adjustment of the bonnet relative to the regulator body. Due to the fluid connection of the outlet through the bonnet tubular portion bore 44, apertures 43, annular space 49 and cross bores 48, the outlet pressure acts against the downwardly facing, annular piston shoulders 57, 58, 59 which are of much greater cross sectional area than the corresponding maximum transverse cross sectional area of the valve seat. When the outlet pressure decreases below a preselected valve, the spring 50 moves the piston downwardly and thereby the juncture of the piston bore portions 37, 38 axially away from the valve seat. As a result, high pressure fluid flows from the inlet 19, through bore portion 38 to pass through the annular clearance space 49 between the valve seat and the piston bore to the apertures 43 and thence to the tubular portion bore 44 to flow to the bonnet outlet 45. At the same time the annular space 49 is in fluid communication with the space 47 and thereby with the piston shoulders 57-59. As the fluid pressure at the outlet 45 increases, the pressure acting against the piston bottom surface increases and the spring 50 is increasingly compressed, the piston moves toward a valve closed position and, upon the fluid pressure at the outlet increasing to the preselected level, blocks fluid flow from the inlet to the annular space 49.
  • To be noted that as the inlet pressure decreases (for example as a result of the emptying of the gas in a gas supply tank), when the piston is it open position, the pressure on the bottom surfaces decreases and the spring [0026] 50 moves the piston in a further opening direction. As a result, as the inlet pressure decreases there is an outlet increase to eliminate the decaying inlet effect. Even though not mentioned, it is to be understood that the movement of the piston to its open position may be of varying axial spacing of the regulator sleeves from one another as a result of the rate of fluid flow required to maintain the desired outlet pressure. Thus, in the piston open position, the valve may just be slightly spaced from the juncture of the piston bore portions 37, 38 to permit a low rate of flow through the regulator to a maximum spacing to permit a higher rate of flow through the regulator.
  • In the event there is leakage flow past the valve seat, there is leakage fluid flow into the annular space [0027] 49 and thence through the cross bores to act against the piston bottom surfaces. Due to the transverse annular area of the piston surface 39 being many times smaller than the combined transverse area of the piston surfaces 57-59 and the valve seat being made of a material, for example plastic, that is more easily deformable than that of the piston, the increasing leakage pressure acting against the piston forces the valve seat to deform sufficiently that there is a new seating of the piston against the valve seat to block bypass leakage flow. This seating action provides an increased resistance to seat leakage caused by vibration. The valve seat is made of a material that if deforms only the amount necessary to form a new seating (annular point of contact of the valve seat with the piston) to block the leakage flow. After the piston moves to its open position subsequent to the new seating, the piston in again moving to its closed position, resumes its new seating.
  • Advantageously, each of the bonnet, including its tubular portion, and the regulator body, including its tubular portion, and the piston is made of a single, unitary piece of material with each the members having its parts integrally joined to one another. As a result, the number of O-rings and the chance of leakage are reduced. Further, the bores of the piston, regulator body, bonnet, other than for the cross bores and apertures [0028] 43, of the first embodiment are coaxial.
  • Referring to FIG. 4, the second embodiment of the invention includes a bonnet (cap) [0029] 12, a piston P and a coil spring 50 that are the same as those of the first embodiment and function in the same manner. The second embodiment also includes a regulator body, generally designated 70, having a bore 73 that is in part defined by a bottom wall 72, and a sleeve 71 that are the same as the same parts of the first embodiment. However, the regulator body of the second embodiment differs from that of the first embodiment in that it incorporates a valve bore 79 for having a shutoff valve, generally designated 80, threaded therein. A passage (bore portion) 78 extends axially through the sleeve 17 and opens to the bore 79. An inlet passage 77 opens to the bore 79 and through the externally threaded neck portion 81, the threaded portion being threadedly mountable to the discharge neck portion of a convention gas tank 82.
  • The shutoff valve [0030] 80 includes a valve body 84 threadedly mounted to the regulator body bore 79 and a valve stem 85 rotatably mounted by the valve body for selectively permitting fluid flow through the valve seat 87 from the passage 77 to the passage 78, the valve seat being mounted in the regulator body bore. There are provided O-rings 88 for forming a fluid seal between the regulator body and the valve body and a fluid seal between the valve stem 89 and the valve body. By incorporating the shutoff valve in the regulator body, no external plumbing is required for connecting the pressure regulator to a high pressure gas tank 82. Thus, the shutoff valve can be used for controlling the flow of high pressure fluid from the high pressure source (gas tank) to the regulator body tubular portion 71.

Claims (20)

    What is claimed is:
  1. 1. A pressure reducing regulator, comprising a regulator body having an upper end and an axial bore opening through the body upper end, the body bore including an axially intermediate bore portion that is in part defined by a body cylindrical wall and a bottom wall remote from the upper end, an axially elongated tubular portion having a bore portion extending axially therethrough, extending within the intermediate bore portion and opening to the intermediate bore portion, the body tubular portion having a first end part remote from the body bottom wall, a bonnet removably mounted to the regulator body and having a top portion with an outlet, a bore opening to the body bore and an axially elongated tubular portion extending within the bonnet bore coaxially with the body tubular portion in axially spaced relationship thereto, the bonnet tubular portion having a first end part axially adjacent to the body tubular portion first end part, a piston axially movably extended within the intermediate bore portion and in fluid sealing relationship to the body wall defining the body bore, the piston being axially movable between a fluid flow open position and a closed position to block fluid flow and having a first axial bore portion with the body tubular portion extending therein, and a second bore portion having the bonnet tubular portion extending therein and being in fluid communication with the piston first bore portion, the bonnet tubular portion having a fluid passageway opening to the outlet and to the piston bore second portion, a valve seat mounted to the bonnet tubular portion first end part to block fluid flow from the body tubular portion to the passageway when the piston is in its closed position and to permit fluid flow from the piston first tubular portion to the piston second tubular portion when the piston is in its open position, first spring means for resiliently urging the piston to move to its open position and second spring means for resiliently retaining the piston in its closed position until the fluid pressure at the outlet decreases below a preselected value.
  2. 2. The pressure reducing regulator of claim 1, wherein the regulator body has a threaded portion, the bonnet has a threaded portion forming a mating fit with the regulator threaded portion to removably mount the bonnet to the body, and a key for retaining the bonnet in selected adjusted threaded positions relative to the regulator body to permit adjusting the axial spacing of the tubular portions relative to one another and thereby an adjustment of the fluid pressure at the outlet.
  3. 3. The pressure reducing regulator of claim 1 wherein each of the bonnet, including its tubular portion, the regulator body, including its tubular portion, and the piston is made of a single, unitary piece of material.
  4. 4. The pressure reducing regulator of claim 1 wherein the regulator body bore has an enlarged diametric bore portion opening to the intermediate bore portion and opening toward the bonnet top portion axially opposite its opening to the intermediate bore portion, the piston has an enlarged diameter first portion in the body enlarged diametric portion and a second piston portion of a smaller diameter than the first piston portion and extending within the body intermediate bore portion to provide a first clearance space therewith, the piston having a bore opening to the passageway and to the clearance space both when the piston is in its open position and in its closed position.
  5. 5. The pressure reducing regulator of claim 4 wherein the piston enlarged diametric portion has a top surface, the bonnet tubular portion has a shoulder abuttable against the piston top surface to limit the movement of the piston toward the bonnet top portion and the piston is abuttable against the bottom wall to limit the movement of the piston away from the bonnet top portion.
  6. 6. The pressure reducing regulator of claim 4 wherein the piston second bore portion is of a larger diameter than the piston first bore portion and at its juncture with the first bore portion provides an annular piston shoulder, the valve seat in the piston closed position being abuttable against the regulator body adjacent to the juncture of the piston first and second bore portions.
  7. 7. The pressure reducing regulator of claim 4 wherein the bonnet tubular portion includes an axially elongated tube part having one end joined to the bonnet top portion and an axially opposite end mounting the bonnet tubular portion first part, the bonnet tubular portion first part including a valve seat mount that, in conjunction with the piston shoulder and the body wall defining the piston second bore portion, forms a second clearance space and has an aperture opening to the second clearance space and the bonnet tubular part, the aperture being part of the passageway.
  8. 8. The pressure reducing regulator of claim 4 wherein there is provided fluid seal means in the piston first bore portion that provides a fluid seal between the body tubular portion and the piston, second fluid seal means in the piston second bore portion axially between the bonnet tubular portion first part and the bonnet top portion for forming a fluid seal between the bonnet tubular portion and the piston, the body wall defining the enlarged diametric bore portion, the piston, the bonnet tubular portion and the bonnet top portion forming an annular cavity and the bonnet has a vent port opening to said cavity.
  9. 9. A pressure reducing regulator, comprising a regulator body having an upper end, an inlet for pressurized fluid and an axial bore opening through the upper end, the body bore having an axially intermediate bore portion, a bonnet removably mounted to the regulator body and having a top portion with an outlet, a bore opening to the body bore and an axially elongated tubular portion extending within the bonnet bore, the bonnet tubular portion having a first end part axially opposite the top portion, a piston axially movably extended within the intermediate bore portion and in fluid sealing relationship to the body wall defining the body bore, the piston having a top surface facing the bonnet top portion and an axially opposite bottom surface with the body intermediate bore portion opening thereto, the piston being axially movable the bonnet tubular portion between a fluid flow open position and a fluid flow blocking position and having a first axial bore portion, and a second bore portion having the bonnet tubular portion extending therein in both of the piston positions and being in fluid communication with the piston first bore portion, first spring means for resiliently urging the piston to move to its open position, the spring means being in abutting relationship to the piston top surface and the bonnet top portion, the bonnet tubular portion having a fluid passageway opening to the outlet and to the piston bore second portion, a valve seat mounted to the bonnet tubular portion first end part and being abuttable against the piston to block fluid flow from the body tubular portion to the passageway when the piston is in its blocking position and to permit fluid flow from the piston first bore portion to the piston second bore portion when the piston is in its open position, and cooperating means for applying pressurized fluid from the inlet to the piston bottom surface and to the first tubular portion when the piston is in its open position and pressurized fluid is being applied at the inlet and blocking the application of fluid under pressure to the piston bottom surface and from the first tubular portion to the second tubular portion when the piston is in its blocking position, the cooperating means at least in part being defined by the piston and regulator body.
  10. 10. The pressure reducing regulator of claim 9, wherein the body bore has an enlarged diametric bore opening to the bonnet top portion and to the body intermediate bore portion, the piston has an enlarged diametric portion in fluid sealing relationship with the body wall defining the body enlarged diametric bore portion and a reduced diameter portion joined to the piston enlarged diametric portion and extending within the body intermediate bore portion to provide an annular clearance space therewith which opens to the piston enlarged diametric portion, the piston bottom surface being provided at least in part by the piston enlarged diametric portion.
  11. 11. The pressure reducing regulator of claim 10 wherein the cooperating means includes a piston cross bore that opens to said clearance space and to piston second bore portion for applying fluid under pressure to the piston enlarged diametric portion when the piston is in its open position and fluid under pressure is applied to the inlet.
  12. 12. The pressure reducing regulator of claim 10 wherein the cooperating means includes second spring means abutting against the piston for constantly urging the piston toward its blocking position.
  13. 13. The pressure reducing regulator of claim 9 wherein the cooperating means includes an axially extending regulator body tubular portion that opens to the inlet, is coaxial with the bonnet tubular portion and extends within the piston first bore portion in axially spaced relationship to the bonnet tubular portion and the valve seat, both in the piston open and blocking positions.
  14. 14. The pressure reducing regulator of claim 13 wherein the piston first bore portion is of a smaller diameter than the piston second bore portion to form an annular shoulder, the valve seat in the blocking position abutting against the piston adjacent to the annular shoulder.
  15. 15. The pressure reducing regulator of claim 14 wherein the bonnet tubular portion includes an axially elongated tubular part having a first end joined to the bonnet top portion and a second end joined to the tubular portion first end part, the tubular portion first end part comprising a valve seat mount having a frustoconical outer surface with a minor base axially remote from the tubular part, the bonnet tubular portion first end part in conjunction with the piston annular shoulder, the valve seat and the piston wall that at least in part defines the piston second bore portion providing an annular clearance space when the piston is in its blocking position, the bonnet tubular part having a bore extending therethrough to open to the outlet and form a part of said passageway and the valve seat mount has an aperture in fluid communication with the bonnet tubular part and said annular clearance space to form a part of said passageway.
  16. 16. The pressure reducing regulator of claim 15, wherein the cooperating means includes a cross bore opening to the above mentioned clearance space and to the body intermediate bore portion and in fluid communication with the piston bottom surface.
  17. 17. The pressure reducing regulator of claim 16 wherein the bonnet bore has an enlarged diametric bore portion opening toward the bonnet top portion and to the body intermediate bore portion to provide an upwardly facing annular shoulder, the piston having an enlarged diametric portion in fluid sealing relationship with the wall that in part defines the body enlarged diametric portion and a second portion joined to the piston enlarged diametric portion and extending within the body intermediate bore portion to provide a second annular clearance with the body wall providing the body intermediate bore portion.
  18. 18. The pressure reducing regulator of claim 16 wherein the regulator body, including its tubular portion, is made of a single integrally joined piece of material, the bonnet, including its tubular portion, is made of a single integrally joined piece of material, the piston is made of a single integrally joined piece of material.
  19. 19. The pressure reducing regulator of claim 16 wherein bonnet and regulator body having cooperating threaded portions to mount the bonnet to the regulator body, an O-ring is provided to form a fluid seal between the bonnet and the regulator body axially between the bonnet top portion and the threaded portions, one of the bonnet and the regulator body having an annular groove axially intermediate the O-ring and the threaded portions, a fluid seal is provided between the piston and the body tubular portion and a fluid seal is provided between the piston enlarged diametric portion and the bonnet tubular portion axially intermediate the bonnet tubular portion first part and the bonnet top portion.
  20. 20. The pressure reducing regulator of claim 16 wherein it is mountable to a container of fluid under high pressure and the regulator body includes a valve bore, a neck portion threadedly mountable to the container and having an inlet, and a second passageway opening to the valve bore for fluidly connecting the neck portion inlet to the body tubular portion and a valve member mounted to the regulator body and extending within the valve bore to selectively permit fluid flow from the neck portion inlet to the body tubular portion and block fluid flow from the neck portion inlet to the body tubular portion.
US10194717 2002-07-12 2002-07-12 Inline pressure reducing regulator Abandoned US20040007269A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US10194717 US20040007269A1 (en) 2002-07-12 2002-07-12 Inline pressure reducing regulator

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US10194717 US20040007269A1 (en) 2002-07-12 2002-07-12 Inline pressure reducing regulator
DE2003125846 DE10325846B4 (en) 2002-07-12 2003-06-06 Pressure-reducing regulator
JP2003271693A JP4246564B2 (en) 2002-07-12 2003-07-08 Pipe vacuum controller device
US10860688 US7159611B2 (en) 2002-07-12 2004-06-03 Inline flow control device

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10860688 Continuation-In-Part US7159611B2 (en) 2002-07-12 2004-06-03 Inline flow control device

Publications (1)

Publication Number Publication Date
US20040007269A1 true true US20040007269A1 (en) 2004-01-15

Family

ID=29780156

Family Applications (2)

Application Number Title Priority Date Filing Date
US10194717 Abandoned US20040007269A1 (en) 2002-07-12 2002-07-12 Inline pressure reducing regulator
US10860688 Active 2023-04-30 US7159611B2 (en) 2002-07-12 2004-06-03 Inline flow control device

Family Applications After (1)

Application Number Title Priority Date Filing Date
US10860688 Active 2023-04-30 US7159611B2 (en) 2002-07-12 2004-06-03 Inline flow control device

Country Status (3)

Country Link
US (2) US20040007269A1 (en)
JP (1) JP4246564B2 (en)
DE (1) DE10325846B4 (en)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1571516A3 (en) * 2004-03-03 2006-05-10 Haldex Brake Corporation Pressure reducing valve
US20060137745A1 (en) * 2004-12-23 2006-06-29 Evolve Paintball Limited Gas pressure regulator
US20070181198A1 (en) * 2006-02-09 2007-08-09 Larsen Todd W Dome-loaded pressure regulators
US20070209703A1 (en) * 2006-03-10 2007-09-13 Fisher Controls International Llc Pressure Reducing Regulator with Adjustable Feature
US20070272307A1 (en) * 2006-05-25 2007-11-29 Patterson Daryll D Sanitary fluid pressure regulator
US20070289643A1 (en) * 2004-11-09 2007-12-20 Masco Corporation Of Indiana Device for dynamic control of a water flow
US20080011361A1 (en) * 2006-06-19 2008-01-17 Tescom Corporation High-Pressure Regulator
US20090126737A1 (en) * 2005-11-09 2009-05-21 Severine Aubonnet Oxygen supplying circuit for an aircraft crew member
EP2166423A1 (en) * 2008-09-19 2010-03-24 Isomatic A/S Balanced fluid valve
US20100101666A1 (en) * 2008-10-28 2010-04-29 Gm Global Technology Operations, Inc. Pressure regulator for hydrogen storage system
EP2247991A2 (en) * 2008-02-28 2010-11-10 Sang Wook Kim Automatic pressure reducing valve
CN103383016A (en) * 2012-05-03 2013-11-06 李耀强 Galvanostat with mother valve and child valve
LU92383A1 (en) * 2014-02-27 2015-08-28 Luxembourg Patent Co Sa Pressure reducer with cap-shaped movable chamber
US20150316162A1 (en) * 2012-12-11 2015-11-05 Aker Subsea As Pressure volume regulator
US20160097362A1 (en) * 2014-10-06 2016-04-07 Hamilton Sundstrand Corporation Variable area orifice for an engine
CN105927741A (en) * 2016-07-06 2016-09-07 成都航天烽火精密机电有限公司 Pressure reducing valve for high-pressure gas
US20160281337A1 (en) * 2015-03-24 2016-09-29 Kane Kougyou Co., Ltd. Proportional pressure reducing valve for waterworks
WO2018041819A1 (en) 2016-08-31 2018-03-08 Luxembourg Patent Company S.A. Compact and pressure compensated gas pressure regulator

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7357153B2 (en) * 2003-11-25 2008-04-15 Hamai Industries Limited Pressure-reducing valve for high-pressure gas cylinders
JP4506496B2 (en) * 2004-11-12 2010-07-21 株式会社ジェイテクト Pressure reducing valve
DE102005052385B4 (en) * 2005-10-31 2008-07-10 Hans Sasserath & Co. Kg pressure reducer
EP1803980B1 (en) * 2005-12-28 2011-12-14 Dan Geva Hollow piston valve
JP2008065727A (en) * 2006-09-11 2008-03-21 Neriki:Kk Pressure reducing valve
WO2009005916A3 (en) * 2007-06-15 2009-12-30 Tescom Corporation 3-way high-pressure air operated valve
US7959010B2 (en) * 2008-03-14 2011-06-14 Cummins Filtration Ip, Inc. Standpipe with integrated regulator valve
US8336575B2 (en) 2009-08-12 2012-12-25 Walter Franklin Guion Fluid pressure control device
EP2464903A4 (en) * 2009-08-12 2013-05-01 Sp Technologies Lc Fluid pressure control device
WO2011100184A1 (en) * 2010-02-10 2011-08-18 3M Innovative Properties Company Pressure-regulating valve
DE102010003016A1 (en) 2010-03-18 2011-09-22 Hyptec Gmbh Pressure regulator for supplying fuel and fuel supply system to a control unit from these pressure regulators
JP5806135B2 (en) * 2012-01-24 2015-11-10 株式会社日本自動車部品総合研究所 Pressure regulating valve
US9518670B2 (en) * 2013-03-15 2016-12-13 David E Albrecht Main stage in-line pressure control cartridge with stepped retainer collar
US9091355B2 (en) * 2013-03-15 2015-07-28 David Albrecht Main stage in-line pressure control cartridge with optional reverse flow function
US20160048138A1 (en) * 2013-03-25 2016-02-18 Ad-Venta Compact Inverted Pressure Regulator for Dispensing a Gas
US9599237B2 (en) 2014-10-07 2017-03-21 Tescom Corporation 3-way inline air operated valve

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2590368A (en) * 1945-03-06 1952-03-25 Bendix Aviat Corp Valve
US2600137A (en) * 1947-12-26 1952-06-10 Bendix Aviat Corp Pressure-regulating valve
US3211175A (en) * 1961-04-03 1965-10-12 Edward H Replogle Valve regulator
US3664369A (en) * 1970-12-09 1972-05-23 Singer Co Pressure reducing regulator
US4476888A (en) * 1981-08-12 1984-10-16 Dr. H. Tiefenbach Gmbh & Co. Overpressure valve
US4667695A (en) * 1984-06-04 1987-05-26 Harold Gold Pressure regulating and on-off valve
US5452741A (en) * 1993-10-01 1995-09-26 Smc Kabushiki Kaisha Pressure reducing valve
US5501247A (en) * 1995-02-17 1996-03-26 Vemco Corporation Pressure regulator with means to block relative rotation of parts during assembly
US5826613A (en) * 1993-05-19 1998-10-27 Georg Fischer Rohrleitungssysteme Ag Flow control valve

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2002450A (en) * 1933-03-09 1935-05-21 George Mfg Company Inc Cylinder cock
US3093155A (en) * 1960-06-20 1963-06-11 Bendix Corp Variable-restriction valve
US3583431A (en) * 1969-02-17 1971-06-08 Cessna Aircraft Co Pressure relief valve
US4924904A (en) * 1986-06-30 1990-05-15 Puritan-Bennett Corporation Adjustable pressure regulator device
EP0458589B1 (en) * 1990-05-22 1995-01-18 R-Tech Ueno, Ltd. Treatment of ocular hypertension with an ocular synergistic combination
US5309934A (en) * 1993-05-21 1994-05-10 Jaeger Robert A Balanced piston fluid valve
US5913328A (en) * 1997-09-15 1999-06-22 Taube; John D. Flow control valve with one piece plug/valve tube sleeve assembly
WO2000004311A1 (en) * 1998-07-16 2000-01-27 Se Woo Conval Co., Ltd. Valve system for fluid pipes
US6170519B1 (en) * 1999-07-28 2001-01-09 Hose Shop, Ltd. Pressure regulator

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2590368A (en) * 1945-03-06 1952-03-25 Bendix Aviat Corp Valve
US2600137A (en) * 1947-12-26 1952-06-10 Bendix Aviat Corp Pressure-regulating valve
US3211175A (en) * 1961-04-03 1965-10-12 Edward H Replogle Valve regulator
US3664369A (en) * 1970-12-09 1972-05-23 Singer Co Pressure reducing regulator
US4476888A (en) * 1981-08-12 1984-10-16 Dr. H. Tiefenbach Gmbh & Co. Overpressure valve
US4667695A (en) * 1984-06-04 1987-05-26 Harold Gold Pressure regulating and on-off valve
US5826613A (en) * 1993-05-19 1998-10-27 Georg Fischer Rohrleitungssysteme Ag Flow control valve
US5452741A (en) * 1993-10-01 1995-09-26 Smc Kabushiki Kaisha Pressure reducing valve
US5501247A (en) * 1995-02-17 1996-03-26 Vemco Corporation Pressure regulator with means to block relative rotation of parts during assembly

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1571516A3 (en) * 2004-03-03 2006-05-10 Haldex Brake Corporation Pressure reducing valve
US20070289643A1 (en) * 2004-11-09 2007-12-20 Masco Corporation Of Indiana Device for dynamic control of a water flow
US7726344B2 (en) 2004-11-09 2010-06-01 Masco Device for dynamic control of a water flow
US7575021B2 (en) * 2004-12-23 2009-08-18 Black Market Sportz Limited Gas pressure regulator
US20060137745A1 (en) * 2004-12-23 2006-06-29 Evolve Paintball Limited Gas pressure regulator
US20090126737A1 (en) * 2005-11-09 2009-05-21 Severine Aubonnet Oxygen supplying circuit for an aircraft crew member
US7669610B2 (en) 2006-02-09 2010-03-02 Tescom Corporation Dome-loaded pressure regulators
US8167001B2 (en) 2006-02-09 2012-05-01 Tescom Corporation Dome-loaded pressure regulators
US20100101665A1 (en) * 2006-02-09 2010-04-29 Todd William Larsen Dome-loaded pressure regulators
WO2007094931A1 (en) 2006-02-09 2007-08-23 Tescom Corporation Dome-loaded pressure regulator
US7870869B2 (en) 2006-02-09 2011-01-18 Tescom Corporation Dome-loaded pressure regulators
US20070181198A1 (en) * 2006-02-09 2007-08-09 Larsen Todd W Dome-loaded pressure regulators
US20070209703A1 (en) * 2006-03-10 2007-09-13 Fisher Controls International Llc Pressure Reducing Regulator with Adjustable Feature
WO2007106374A3 (en) * 2006-03-10 2007-11-01 Fisher Controls Int Pressure reducing regulator with adjustable feature
CN101401050B (en) 2006-03-10 2012-03-28 费希尔控制产品国际有限公司 Pressure reducing regulator with adjustable feature
US7828009B2 (en) 2006-03-10 2010-11-09 Tescom Corporation Pressure reducing regulator with adjustable feature
US20070272307A1 (en) * 2006-05-25 2007-11-29 Patterson Daryll D Sanitary fluid pressure regulator
US20080011361A1 (en) * 2006-06-19 2008-01-17 Tescom Corporation High-Pressure Regulator
US7757710B2 (en) 2006-06-19 2010-07-20 Tescom Corporation High-pressure regulator
EP2247991A4 (en) * 2008-02-28 2012-06-27 Kim San Wook Automatic pressure reducing valve
EP2247991A2 (en) * 2008-02-28 2010-11-10 Sang Wook Kim Automatic pressure reducing valve
EP2166423A1 (en) * 2008-09-19 2010-03-24 Isomatic A/S Balanced fluid valve
US20110174394A1 (en) * 2008-09-19 2011-07-21 Isomatic A/S Balanced fluid valve
WO2010031400A1 (en) * 2008-09-19 2010-03-25 Isomatic A/S Balanced fluid valve
US9074703B2 (en) 2008-10-28 2015-07-07 GM Global Technology Operations LLC Pressure regulator for hydrogen storage system
US9823668B2 (en) 2008-10-28 2017-11-21 GM Global Technology Operations LLC Pressure regulator for hydrogen storage system
US20100101666A1 (en) * 2008-10-28 2010-04-29 Gm Global Technology Operations, Inc. Pressure regulator for hydrogen storage system
CN103383016A (en) * 2012-05-03 2013-11-06 李耀强 Galvanostat with mother valve and child valve
US20150316162A1 (en) * 2012-12-11 2015-11-05 Aker Subsea As Pressure volume regulator
US9970559B2 (en) * 2012-12-11 2018-05-15 Aker Solutions As Pressure volume regulator
LU92383A1 (en) * 2014-02-27 2015-08-28 Luxembourg Patent Co Sa Pressure reducer with cap-shaped movable chamber
CN106104117A (en) * 2014-02-27 2016-11-09 卢森堡专利公司 Pressure reducer with cap-shaped movable chamber
WO2015128234A1 (en) * 2014-02-27 2015-09-03 Luxembourg Patent Company S.A. Pressure reducer with cap-shaped movable chamber
US20160097362A1 (en) * 2014-10-06 2016-04-07 Hamilton Sundstrand Corporation Variable area orifice for an engine
US20160281337A1 (en) * 2015-03-24 2016-09-29 Kane Kougyou Co., Ltd. Proportional pressure reducing valve for waterworks
CN105927741A (en) * 2016-07-06 2016-09-07 成都航天烽火精密机电有限公司 Pressure reducing valve for high-pressure gas
WO2018041819A1 (en) 2016-08-31 2018-03-08 Luxembourg Patent Company S.A. Compact and pressure compensated gas pressure regulator

Also Published As

Publication number Publication date Type
US7159611B2 (en) 2007-01-09 grant
JP2004038982A (en) 2004-02-05 application
DE10325846B4 (en) 2013-09-19 grant
DE10325846A1 (en) 2004-01-22 application
US20040216781A1 (en) 2004-11-04 application
JP4246564B2 (en) 2009-04-02 grant

Similar Documents

Publication Publication Date Title
US3211175A (en) Valve regulator
US3120243A (en) Flow regulating valve with extended movement
US3211174A (en) Pressure relief or blowdown valve
US5285810A (en) Pressure-reducing regulator for compressed natural gas
US6079526A (en) Damping force control type hydraulic shock absorber
US6042091A (en) Shock absorber
US2599577A (en) Balanced fluid pressure regulating valve
US5875817A (en) Digital gas metering system using tri-stable and bi-stable solenoids
US3765604A (en) Mixing faucet
US5522421A (en) Fluid pressure regulator
US4341370A (en) High pressure, three stage, balanced valve
US4586533A (en) Non-flowing modulating pilot operated relief valve
US4474208A (en) Safety valve
US5232273A (en) Brake system pump with a damper chamber with leaf spring and cup closure
US2994343A (en) Metering valve
US6354319B1 (en) Low differential, pilot operated fluid pressure regulation apparatus and method
US4850392A (en) Double poppet relief valve
US4609008A (en) Non-flowing pressure responsive pilot valve
US2342659A (en) Loading regulator
US4693267A (en) Self-venting pressure reducing regulator
US5666990A (en) Attachment member for engaging with different tire valves
US2769454A (en) Pressure control fittings
US5299598A (en) Check valve
US20070023087A1 (en) Screwable check valve
US4195552A (en) Pressure reducer and flow control valve

Legal Events

Date Code Title Description
AS Assignment

Owner name: TESCOM CORPORATION, MINNESOTA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LARSEN, TODD W.;REEL/FRAME:013097/0931

Effective date: 20020708