GB2024999A - Pressure Regulators - Google Patents
Pressure Regulators Download PDFInfo
- Publication number
- GB2024999A GB2024999A GB7923465A GB7923465A GB2024999A GB 2024999 A GB2024999 A GB 2024999A GB 7923465 A GB7923465 A GB 7923465A GB 7923465 A GB7923465 A GB 7923465A GB 2024999 A GB2024999 A GB 2024999A
- Authority
- GB
- United Kingdom
- Prior art keywords
- piston
- pressure regulator
- housing
- spindle
- chamber
- 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.)
- Granted
Links
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D16/00—Control of fluid pressure
- G05D16/04—Control of fluid pressure without auxiliary power
- G05D16/10—Control of fluid pressure without auxiliary power the sensing element being a piston or plunger
Landscapes
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Control Of Fluid Pressure (AREA)
Abstract
A differential piston 4 having a profiled waist or intermediate portion 5 defined between two portions of different radius is slidably mounted on a spindle 6 within a housing having inlet and outlet ports 2, 3. The piston is urged by a spring assembly 2 to allow communication between the inlet and outlet ports through an annular control port formed between the waisted portion of the piston and the interior of the housing. The action of an incoming high pressure fluid at the waisted portion and against the piston portion of greater radius displaces the piston against the action of the spring assembly to maintain a substantially constant pressure and hence flow in a branch line connected to the outlet port 3. Means are provided for adjusting the spring assembly and thereby the operating range of the regulator. <IMAGE>
Description
SPECIFICATION
Pressure Regulators
The present invention concerns pressure regulators for reducing and regulating pressure in branch lines connected to main pressure lines, the pressure in the main lines being too high for direct application.
According to the present invention a pressure regulator comprises a housing, a piston slideable in the housing, a pair of annular chambers in the housing about the piston, one of the chambers having an inlet for a fluid at high pressure, the other chamber having an outlet for the fluid, an annular control port formed between cooperating portions of the piston and housing and providing communication between the chambers, the piston presenting an increased surface area to the fluid within said other chamber such that fluid entering said other chamber acts to urge the piston into a position to close the control port, and adjustabie spring means acting on the piston to oppose said fluid action to maintain the control port in an open condition consistent with a required pressure at the outlet from said other chamber.
The invention will be described, by way of example, with reference to the accompanying drawings; in which: Fig. 1 is a sectional view of an embodiment of a pressure regulator; and
Fig. 2, comprising 2a and 2b, is a view of a modified end of the regulator shown in Fig. 1.
A pressure regulator comprises a housing 1 having inlet and outlet ports 2 and 3 respectively with a hollow piston 4 slidable within the bore of the housing. One end of the piston 4, the upper end as shown in the drawing, is of a smaller diameter than the opposite lower end. The two end portions are joined by an integral waist 5 having a bore therethrough to receive a spindle 6 which extends coaxially the length of the housing.
The bore of the housing is profiled to cooperate with the piston. An annular inlet chamber 7 communicates with the inlet port 2. The chamber 7 is arranged off-centre with respect to the axis of the piston whereby to produce a swirl flow path for fluid entering the chamber through the inlet 2.
An outlet chamber 8 communicates with the outlet port 3 and is separated from the inlet chamber by an inwardly directed flange or lip 9 which can engage a face 10 on the piston.
The upper and lower ends of the piston are in sliding, sealing engagement with cylindrical portions of the bore. Preferably, the cylindrical portions are formed by liners 11, 12 conveniently formed from stainless steel, to reduce wear and friction. The liner 11 is positioned between a lip 13 and an end cap 14. The liner 12 is positioned between a similar lip 1 5 and a sandwich plate 1 6 which is secured by countersunk screws 1 7 to the housing. A second larger end cap 1 8 is in turn secured to the sandwich plate 1 6 and the housing by a stud, plain washer, spring washer and nut assemblies 1 9.
A seal ring assembly 20 is located about the
ends of the piston to cooperate with the stainless
steel liners. Each assembly comprises an
elastomeric O-ring, suitably a rubber O-ring
surrounded by a plastics ring, the preferred
plastics material being PTFE.
A spring assembly 21 is located within the larger
diameter end of the piston. Conveniently the
assembly comprises coaxial inner and outer coil
springs 22 and 23 respectively. The springs are
accommodated and positioned between stepped
faces on the piston and stepped faces on a spring
cap 24 which is supported by an adjustable nut
25 in threaded engagement with a thread at the
end of the spindle 6. A locknut 26 is also provided
on the threaded end of the spindle. The adjacent
end of the spindle 6 is located in central socket in
the end face of the end cap 1 8. This end face is
further provided with openings 27 which are
concealed beneath a resiliently deformable end
cover 28.
The opposite end of the spindle is also
threaded and is located in a bore in end cap 14. A
lock nut 29 on the spindle bears against the inner
face of the end cap and the end of the spindle
protruding through the end cap 14 is secured by
screw collar 30 with a tension pin 31 extending
through aligned diametrical apertures in the
spindle and the collar. The end cap 14 is secured
to the housing by stud, plain washer, spring
washer and nut assemblies 32 and the end cap is
also provided with openings 33 which are
concealed beneath a resiliently deformable end
cover 34. A channel 35 formed on the inner face
of the end cap communicates with the openings.
The waist 5 of the piston is profiled as shpwn in the drawing. Thus, in moving in a direction from the smaller diameter end of the piston to the larger diameter end the waist has an inwardly sloping surface 36 which is radiused at its base to merge smoothly with an outwardly sloping surface 37. The waist is profiled so as to present a smooth continuous surface to the fluid.
Preferably, the surfaces 36 and 37 are inclined at 45 to the longitudinal axis of the regulator.
In its inoperative condition the piston 4 is urged by the spring assembly 21 into an end position at which the end of the smaller diameter portion abuts against the inner face of the end cap 1 4. In this position of the piston the face 10 slides out of engagement with the flange 9 to provide an annular control port between the chambers 7 and 8. When the inlet port is coupled to a high pressure line the incoming high pressure fluid swirls around in the chamber 7 and passes into the outlet chamber 8 through the annular port formed between the separated face 10 and the flange 9. The fluid entering the chamber 8 tends to react on the faces 36 and 37 in opposite directions. The reaction at the face 36 tends to urge the piston towards the end cap 14 while the reaction at the face 37 tends to urge the piston in the opposite direction towards the end cap 18.
The smooth profile of the waist avoids any abrupt movement of the piston and the effective
operating area of the piston is given by the
annulus between the radii r1 and r2 where r, is the
radius of the sealing face of the flange 9 and r2 is
the radius of the sealing face of the liner 12. The
piston will achieve a stable balance or equilibrium
position at which the pressure on the piston is
such as to maintain a substantially constant gap
at the annular port between the chambers 7 and
8. The extent of this gap is determined by the
tension of the spring assembly and this can be set
by appropriate adjustment of the nut 25 on the
spindle. The spring lengths and loads can be
calculated and selected for different operating
inlet and outlet pressures.As examples, the spring
assembly at the left hand side of the drawing is
for a low output regulator while that at the right
hand side of the drawing is for a high output
regulator. The low output regulator can receive an
inlet pressure range from 140 to 240 p.s.i. with
an outlet pressure setting range from 80 to 120
p.s.i. Such a regulator is suitable for a nominal
flow of 100 gallons per minute. Corresponding
figures for the high output regulator with the
same inlet pressure range can be 110 to 134
p.s.i. outlet range and a nominal flow of 200 gailons/minute.
The spring assembly in Fig. 1 comprises two
coaxial coil springs. Clearly, the assembly can be
modified to include more than two springs and
thereby increase the operating pressure range of
the regulator. For example, a third coil spring
could be accommodated in the larger diameter
end of the piston and the regulator could then
operate an-an outlet pressure in the region of 1 50 p.s.i.
It is to be noted that d gap 38 is provided
between the faces of the piston and the liners at
the side of each sealing ring assembly directed
towards the respective chambers 7 and 8. The
gaps enable the pressure fluid passing through
the housing to scour away any dirt or debris
which might otherwise damage the seals or
increase their frictional resistance. The portions of
the piston at the opposite sides of the sealing ring
assemblies are in substantially sliding
engagement with the liners to prevent lateral
movement or play.
Seepage-of fluid can occur around the ends of
the piston which could result in undesirable
pressure build-ups. Any such seepage can escape
through the openings 27 and 33 in the respective
end caps 18 and 14.
Figs. 2a and 2b show'a modification for
adjusting the pressure of the springs, Fig. 2b
being a view at right angles to Fig. 2a.
The upper end cap 14 in Fig. 1 is modified in
Figs. 2a and 2b whereby the piston rod 6 is
slidable in the end cap. For this purpose, the bore
in the end cap to receive the piston rod 6 is lined
with a bush 50 to permit sliding movement of the
piston rod. The end of the piston rod protruding
beyond the end cap is threaded and received in
threaded boss 51 which is fixedly secured to the
base of a U-shaped member 52. The piston rod is
secured by a locknut 53. The opposite end of the
piston rod 6 is extended to maintain support
within the end cap 18.
The U-shaped member 52 is arranged between two substantially identical inverted U-shaped members 54 which are mounted on four pillars 55 on the end cap 14. The members 54, pillars 55 and the end cap are secured to the housing 1 by studs or bolts (not shown).
Two spaced apart plates 56 are fixedly secured to the upper ends of the members 54, the plates passing between the limbs of the U-shaped member 52, and constituting a support for a cam follower 57. The cam follower 57 is carried on a spindle 58 which is journalled in the plates 56.
A spindle 59 passes through aligned bores at the free ends of the limbs of the U-shaped
member 52 and a cam 60 is mounted on the spindle 59 to engage the cam follower 57. The cam is actuated and moved to turn about the spindle 59 by means of a lever or handle 61. In the illustrated embodiment the cam is movable between three operative positions as indicated and at which the cam surface is notched and profiled to match the curvature of the cam follower. Operation of the cam effects a jacking
action on the piston rod 6 to change the tension of the spring assembly and thereby the operating pressure of the regulator.
Examples of the use of the described regulator are for reducing and regulating the pressure in
branch lines of foam and water fire-fighting
sytems and airfield crash tenders where the main operating pressure is too high for direct application.
Claims (10)
1. A pressure regulator comprising a housing, a piston slideable in the housing, a pair of annular chambers in the housing about the piston, one of the chambers having an inlet for-a fluid at high
pressure, the other chamber having an outlet for the fluid, an annular control port formed between
cooperating portions of the piston and the
housing and providing communication between the chambers, the piston presenting an increased
surface area to the fluid within said other
chamber such that fluid entering said other chamber acts to urge the piston into a position to
close the control port, and adjustable spring
means acting on the piston to oppose said fluid
action to maintain the control port in an open
condition consistent with a required pressure at
the outlet from said other chamber.
2. A pressure regulator as claimed in claim 1 in
which the piston has a first portion within said
one chamber joined to a second portion within
said other chamber by a waist portion presenting
a smooth continuous surface to the fluid, the
diameter of the first portion being smaller than
the diameter of the second portion.
3. A pressure regulator as claimed in claim 2 in
which the diameter of the waist portion decreases
progressively from the respective first and second
piston portions.
4. A pressure regulator as claimed in claim 2 or 3 including a spindle passing axially through the piston and journalled in the opposite ends of the housing.
5. A pressure regulator as claimed in claim 4 in which the spring means comprises a spring assembly located within the second portion of the piston between an end of said second portion adjacent the waist portion and a cap on the spindle.
6. A pressure regulator as claimed in claim 5 in which the cap is displaceable axially along the spindle to vary the tension of the spring assembly.
7. A pressure regulator as claimed in claim 5 including jacking means mounted on one end of the housing and coupled to the spindle to axially displace the spindle to vary the tension of the spring assembly.
8. A pressure regulator as claimed in claim 5, 6 or 7 in which the spring assembly comprises two or more coaxial coil springs.
9. A pressure regulator substantially as herein described with reference to and as illustrated in
Fig. 1 of the accompanying drawings.
10. A pressure regulator substantially as herein described with reference to and as illustrated in
Fig. 1 when modified by the arrangement in Fig. 2 of the accompanying drawings.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB7923465A GB2024999B (en) | 1978-07-08 | 1979-07-05 | Pressure regulators |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB7829251 | 1978-07-08 | ||
GB7923465A GB2024999B (en) | 1978-07-08 | 1979-07-05 | Pressure regulators |
Publications (2)
Publication Number | Publication Date |
---|---|
GB2024999A true GB2024999A (en) | 1980-01-16 |
GB2024999B GB2024999B (en) | 1983-04-27 |
Family
ID=26268156
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
GB7923465A Expired GB2024999B (en) | 1978-07-08 | 1979-07-05 | Pressure regulators |
Country Status (1)
Country | Link |
---|---|
GB (1) | GB2024999B (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1873607A1 (en) * | 2006-06-30 | 2008-01-02 | Luxembourg Patent Company S.A. | Pressure regulator for high pressure gas |
-
1979
- 1979-07-05 GB GB7923465A patent/GB2024999B/en not_active Expired
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1873607A1 (en) * | 2006-06-30 | 2008-01-02 | Luxembourg Patent Company S.A. | Pressure regulator for high pressure gas |
EP1873607B1 (en) | 2006-06-30 | 2017-04-12 | Luxembourg Patent Company S.A. | Pressure regulator for high pressure gas |
Also Published As
Publication number | Publication date |
---|---|
GB2024999B (en) | 1983-04-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US2342659A (en) | Loading regulator | |
US4493335A (en) | Shear valve | |
US4092998A (en) | Automatic pressure regulator | |
KR900003570A (en) | Gas Pressure / Gas Flow Compensation Direct Acting Pressure Regulator | |
US3722536A (en) | Monitor pressure regulator assembly | |
US3653631A (en) | Ball valve construction | |
AU2003227774A1 (en) | Pneumatic, liquid-dispensing gun | |
KR100398080B1 (en) | Pressure Flow Rate Control Valve | |
US2326825A (en) | Altitude-controlled regulator | |
US5054517A (en) | One-way restrictor | |
US4106824A (en) | Hydrostatic supporting device | |
US5718410A (en) | Small flow control valve with cartridge type seating arrangement | |
US4185771A (en) | Water mixing valve with temperature regulation, temperature setting and volume control | |
US5056550A (en) | Pilot regulator for valves | |
US4325406A (en) | Continuous fluid pressure control device and system | |
US2710163A (en) | Gas pressure regulator | |
US3633608A (en) | Gas pressure regulating valve | |
US4313460A (en) | Pilot valve | |
US3472264A (en) | Fluid pressure controller with adjusting means | |
GB2024999A (en) | Pressure Regulators | |
US2982294A (en) | Control valve | |
GB1593890A (en) | Fluid pressure responsive valve | |
US4253484A (en) | Valve operator | |
US4051870A (en) | Single handle mixer valve | |
EP1845430B1 (en) | Pressure reducing valve |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
732 | Registration of transactions, instruments or events in the register (sect. 32/1977) | ||
PCNP | Patent ceased through non-payment of renewal fee |