Gas pressure regulator
(57) Abstract:The invention relates to automatic control and can be used in pneumatic systems for various purposes. The technical result of the invention is the extension of the range of output pressures towards lower values. The regulator has a housing 1 with an inlet 2 and outlet 3 cavities separated by the first valve 5. The first sensor element in the form of a stepped piston 6 and the second sensing element piston 10 associated with the second 15 and third valves 19, cause the reaction to the output pressure and by filling-operaniuni cavities provide a correction output pressure and precise control. The ratio of the structural parameters allows to obtain the minimum possible output pressure, and the formula, you can determine its value. The technical result of the invention is achieved by applying these ratios and formulas. 1 Il. The invention relates to automatic control and can be used in pneumatic systems for various purposes.A known gas pressure regulator, comprising a housing placed between the input and vikaparshina, the lower stage of which is connected with the first valve and forms with greater tread and casing a first chamber which is communicated through an orifice to the atmosphere. There is a second sensitive element in the form of a piston, a spring-loaded tasks, and a second chamber which is communicated with the output cavity and through the second valve with the first cavity. Moreover, the piston is placed in the sleeve that is installed in the housing between the piston and the larger step of the stepped piston and provided with a seat of the second valve, which is located in the piston, the second chamber is formed by a piston and sleeve, which made the saddle of the third valve, placed in the sleeve, which forms a greater degree of the stepped piston of the third cavity. While the second and the third cavity communicated through the third valve, and in the initial position of the sleeve contact is connected with the piston and the large step of the stepped piston, the third valve is pressed against its seat by the piston, and the third connection of the valve with its seat in the position of their contact is made with guaranteed leak.Listed above are the essential features of the prototype provide increased precision regulator, but there is uncertainty lower value of the output pressure is rasshirenie range of output pressures towards lower values by offering correlations of structural parameters of the controller, determining the minimum outlet pressure, and the formula that determines the value of the minimum outlet pressure, i.e., the set of features of the first claim is supplemented by the following new significant features. There are ratios
1, where F is the effective annular area of the stepped piston, perceiving the pressure in the third cavity;
Fin- the effective area of the sleeve
1, where hand- release of the first valve in the initial position;
hkr- critical (minimum acceptable) release of the first valve, in which the resistance of the output line is set to the critical output pressure Pkrsufficient impact on the area F to the support lines hkrand (Tkr+ KX) 1, where Tnand Tkr- efforts on the first valve respectively supplies a regulated mode, and when the release valve on the value of hkr;
K - spring stiffness job;
X - total spring compression job at moving the sleeve from the position corresponding to hkruntil it stops in the housing and a second sensing element of the stop positions in the sleeve to the position corresponding to the beginning of the movement of the second claerbout lower value of the output pressure, and the minimum value of the output pressure PN. minis determined by the formula
PN. min= ..Conclusion correlation parameters and formulas for minimum output pressure.The friction force when the output is not selected. It is assumed their account with the appropriate signs as components of the considered forces.Let's agree that the process controller output from the reference position on the regime with the output pressure Pnis when the impedance of the output line (for example, when installing expenditure washers), providing the maximum gas flow.The technical result of the invention is the extension of the range of output pressures towards lower values.In the initial position of the regulator (the regulator is configured, but the input pressure is not filed) must be a minimum required Randspring task, in which the first valve can be depressed by the value of handunder the condition of Tand= RI.< / BR>There is some minimum value of releasing hkr(critical), wherein supplying the output pressure in the output cavity may be some minimal the stage piston, and with it the first valve to its release hkr. The value of hkrmeet and Tkr= RCR.hkrcalculated using known formulas taking into account the gas flow.Thus, the first condition for the implementation of the process controller output to the mode of regulation is the ratio
The second condition of the controller output to the mode control pressure Pnis force the bushings on the stepped piston, at least, to increase the pressure to a value of Pkr, i.e., PkrFPkrFinor 1 (2) where Fin- the effective area of the sleeve.Moreover, the working conditions of the regulator (sleeve at Pnshould move all the way into the building) should be FinF2(3) where F2- the area of the second sensing element.Further movement of the first valve on the value of
h = hn- hkrwhere hn- the valve stroke corresponding to the pressure Pnand the force on the valve Tnis increasing efforts on the first valve is set to the value T = Tn- Tkr.The output pressure increases on the value of R = Rn- Rkr.Prince the first valve on the value of h, i.e., to the efforts of Tn:
Since R = Rn- Rkrand Pn= , where Rnthe spring force jobs at Pn;
Pkr= ,the expression(4) can be written
- F T.. (5)
Since Rn= Rkr+ FOR (Xin+ X2), where Xin- move the sleeve from the position corresponding to hkruntil it stops in the housing (in the direction of compression springs job);
X2- the displacement of the second sensor element out of the way into the sleeve in the position corresponding to the beginning of the movement of the second valve;
Rkr= Tkrwhen the designation Xin+ X2= X, the expression (5) takes the form
- F T
(Tkr+KX) - TkrT ..Taking into account T + Tkr= Tnfinally write
(Tkr+KX) 1. (6)
The relation (3) is a common condition for any range of output pressures. Ratio (1), (2) and (6) must be considered when designing, solving the task of expanding the range of output pressures towards lower values.From the relation (1) implies that if hand> hkrthe first valve is pressed in the initial position with a surplus due to the excessive force of the spring job that regulated the PE the minimum Pn.From (2) that upon reaching the output and the third cavity pressure Pkra stepped piston having the ability to move without force action sleeve, continues with Fin< F to test this effect, i.e., the force setpoint spring and Rnincreased. The equal sign in this ratio also corresponds to the minimum of Pn.The expression (4), from which is derived the relation (6) has on the left of the multiplier R. decrease (Pn= Pkr+ P) corresponds to the decrease of the Pnand the sign of equality in relations (4) and (6) meets the minimum Pn.Thus, smaller values of the expressions (1), (2) and (6) corresponds to the more technical result.Designing it is advisable to start with assignments efforts on the first valve based on the required effort sealing, possibly taking into account the dynamics, determination of hkrand the choice of F2. Next, taking into account the relations (2), (3) and (6) designate Fin, F.Itself the minimum value of PN. minis defined as follows.The minimum possible force Rncompression springs
RN. min= Tkr+ KH.The gas pressure regulator is schematically shown in the drawing.The regulator includes a housing 1 with an inlet 2 and outlet 3 cavities, separated by a saddle 4 with the first valve 5, the first sensor element in the form of a stepped piston 6, the smaller the degree of which is connected through a rod 7 with the first valve and forms a greater degree and the housing, the first cavity 8, is connected through a throttle 9 with the atmosphere, a second sensing element in the form of a piston 10, placed in the sleeve 11 forming a second cavity 12 and the spring-loaded 13 jobs. The second cavity 12 is communicated through the saddle 14 and located in the piston 10 of the second valve 15, through the channel 16 in the adapter 17 with the first cavity 8. The sleeve 11 is formed with a greater degree of piston 6 third cavity 18, which through the third valve 19 with the saddle 20 is communicated to the second cavity 12. Channel 21 and the second cavity 12 is in communication with the output cavity 3. Contact the valve 19 with the saddle 20 is made with a guaranteed leak.Area Finsleeve 11 is shown conventionally. To determine the effective area Finconsider Glca 11 pojate to the piston 6 by the spring 13 job through the piston 10. The first valve 5 is pressed against the seat 4 by the piston 6 via the shaft 7 in the particular case by the value of hkr. The valve 19 is pressed against the seat 20 of the piston 10 and the valve 15 is drawn in to the seat 14 by a spring with a gap X2relatively hard stop in the piston 10. The sleeve 11 has a course of Xinin the direction of the compression spring 13 jobs.When submitting the environment in the input cavity 2 and the corresponding output resistance line and compressing valve (hkrin output 3, the second 12 and third cavities 18, the pressure begins to increase to a certain critical value of Pkr. At this pressure the piston 6 can blank the first cavity 8 has no impact sleeve 11 to move, additionally pressing the first valve 5. The pressure in the cavities 3, 12 and 18 increases to the required set pressure Pnin which the sleeve 11 and the piston 10 is moved on values of Xinand X2accordingly, and depending on the magnitude of pressure Pnyou can open seat 14 and a filling the first cavity 8.When the original release of the first valve 5 by the value of hkrwhen expressions (1), (2) and (6) equal to one, and at a minimum Xinand X2the output pressure Pnwill be minimal wolnym due to the reaction on the output pressure of the pistons 6 and 10, possible recharge and operatiunea first cavity 8 and the automatic movement of the first valve 5. Some changes in outlet pressure steady-state process are tracked and the third cavity due to the guaranteed leaks from valve 20 valve 19. GAS PRESSURE REGULATOR comprising a housing placed between the input and output cavities of the first valve, the first sensor element in the form prescribed in the case of the stepped piston, the smaller the degree of which is connected with the first valve and forms with greater tread and casing a first chamber which is communicated through an orifice to atmosphere, the second sensitive element in the form of a piston, a spring-loaded tasks, and a second chamber which is communicated with the output cavity and through the second valve with the first cavity, and the piston is placed in the sleeve, set in the casing between the piston and the larger step of the stepped piston and provided with a seat of the second valve, which is located in the piston, the second chamber is formed by a piston and sleeve, which made the saddle of the third valve, placed in the sleeve, which forms a greater degree of the stepped piston of the third cavity, and the second is information step of the stepped piston, the third valve is pressed against its seat by the piston, and the third connection of the valve with its seat in the position of their contact is made with guaranteed leak, wherein the design parameters are assigned in accordance with ratios
F / Fin1 ,
where F is the effective area of the stepped piston, perceiving the pressure in the third cavity;
Fin- the effective area of the sleeve
hand/ hkr1 ,
where hand- release of the first valve in the initial position;
hkr- critical (minimum acceptable) release of the first valve, in which the resistance of the output line is set to the critical output pressure Pkrsufficient impact on the area F to maintain the hkr;
(Tkr+ KX) 1,,
where Tn, Tkr- efforts on the first valve respectively supplies a regulated mode, and when the release valve on the value of hkr;
K - spring stiffness job; X is the total spring compression job at moving the sleeve from the position corresponding to hkruntil it stops in the housing and a second sensing element of the stop positions in the sleeve to the position corresponding to the beginning of p the values of the ratios correspond to lower values of the output pressure, and the minimum value of the output pressure PNMPis determined by the formula
Pnmin= (Tkr+ KX) / F2.
FIELD: hydraulic and pneumatic automatics, namely regulation of pressure of natural gas at outlet of gas distributing stations.
SUBSTANCE: regulator includes outer cylindrical housing, swirling chamber coaxial to said housing, designed for energy separation and having annular duct for drawing off hot flow and unit for controlling cross section of tangential nozzle inlet of compressed air in chamber. Said unit is arranged between diaphragm and swirling chamber. Recovering swirl ejector is arranged directly behind diaphragm in cold end part of chamber. Controlling unit, namely valve unit is in the form of hollow cylinder moved in lengthwise direction by means of rod of servo drive. At side of diaphragm cylinder engages with outlet cross section of nozzle inlet through lengthwise tangential ducts in wall of inlet collector embracing outer wall of said valve. Outlet of duct for drawing off hot flow to side of cold end of chamber and to side of housing of nozzle inlet is connected with collector for supplying hot flow to ejector. The last is in the form of tangential ducts in lateral wall of duct for drawing off cold flow. Behind mixing passage of ejector and lateral branch of mixed flow said servo drive of regulator is arranged.
EFFECT: enhanced operational reliability, enlarged functional possibilities of one-aggregate gas pressure regulator, improved accuracy of regulation due to effective self-heating and dynamic balance of shut-off pair.
3 cl, 3 dwg
FIELD: hydraulic and pneumatic engineering.
SUBSTANCE: device has body with coaxially placed two serially opened locking organs. Coaxially to body guiding cylinder perforated with through apertures is fixed to first locking organ, placed with possible displacement relatively to guiding cylinder and interaction with saddle and stationary support. Second locking organ is made in form of decreased cope of the first one, provided with guiding cylinder, fixed to analogical cylinder of first locking organ on the side of flow output. First locking organ is made in form of hollow barrel moved along outer surface of guiding cylinder with unloading apertures in its bottom. Hollow barrel I loaded with back action spring. The latter is placed between its bottom and body. Second locking organ is loaded with back action spring, placed between its bottom and bottom of first locking organ. Saddle for first locking organ is placed on the side of flow output. Bottom of second locking organ is placed on the side of flow output. Bottom of first locking organ is connected to servo through rod. On each saddle of guiding cylinders of locking organs on the side of flow outputs protective element is placed. Protective element is in contact with front edge of barrel and is made in form of for example moveable ring spring-loaded relatively to saddle. This ring envelopes saddle and covers stationary compaction of locking couple in its open position on the side of the flow. Ring is provided with unloading apertures and limiter of movement in form of for example removable brackets. Brackets are evenly placed along circle in amount no less than three and fixed at the end of saddle. Servo is made in form of pneumatic cylinder adjuster coaxial to the body. Said cylinder is mounted outside gas flow and contains moving piston. Piston separates hollows of controlling and output pressures. In hollow of said pressure said rod connected to piston is placed. On the opposite side piston is supported by pusher. Pusher is mounted coaxially with its possible contact to sensor of position of locking organs ad coaxial to pusher of limiter of their movement, moved manually or automatically.
EFFECT: higher durability, broader functional capabilities.
FIELD: gas industry.
SUBSTANCE: device has controlling electromagnetic valve with inlet saddle, connected to gas-feeding channel, adjusting organ, driven by electric magnet, and outlet saddle, low pressure hollow with branch channel and separated from it by fixed saddle and cutting latch high pressure hollow, cylindrical chamber with moving element, interacting through pusher with cutting latch and forming in chamber on the side of pusher a working hollow, connected to controlling valve hollow, and on the opposite side an auxiliary hollow connected to atmosphere with mechanical spring positioned on it and adjusting element for given low pressure. Outlet saddle of controlling valve is connected via channel to low pressure hollow. Pusher is made in end, which kinematically interacts with cutting latch of moving saddle, connected by auxiliary hollow through aperture in moving element and pusher.
EFFECT: higher efficiency.
2 cl, 2 dwg
SUBSTANCE: device has outer cylindrical body, vortex chamber coaxial to the latter for energy separation with circular channel for intake of hot flow and assembly for adjusting cross-section of tangential nozzle intake of compressed gas into chamber, positioned between diaphragm and chamber, and also utilizing ejector, while adjusting assembly, valve in particular, is made in form of diaphragm body moved in longitudinal fashion by servo rod, and interacting with outlet cross-section of nozzle intake via longitudinal tangential channels on the wall of cold end of vortex chamber, enveloping outer wall of valve, while channel for intake of hot flow to cold end of chamber by its outlet is connected to inlet of hot flow into ejector, while outer cylindrical body with side inlet of compressed gas and shut on the side of outlet of servo rod and hot end of vortex chamber has a spin diffuser directed along hot flow, with turbulence promoter, intermediate wall, held in flange groove of outer body, and also - outlet extending wall in such a way, that in ring-shaped area, forming an inlet collector across from side inlet of compressed gas, coaxially to outer body ejector pipes rigidly connected to walls are positioned with nozzles for outlet of hot flow in parallel to output of cold flow from diaphragm. Rod, mounted strictly along axis of vortex chamber, on the side of output of cold flow by ball support is connected to intersection of body of diaphragm and valve.
EFFECT: higher reliability, higher durability, higher efficiency.
4 cl, 1 dwg
FIELD: fluid-pressure automatics.
SUBSTANCE: device comprises tubular housing and spring-loaded self-centering sensor made of a truncated cone. The sensor and housing define a ring slot that converges in the direction of flow. The baffle inside the housing has throttling slot. The pipe is connected to the sensor at its center. A part of the pipe is made for permitting cooperation with the relief space downstream of the throttling slot. The inlet space of the housing is connected with the space upstream of the throttling slot through the by-pass that receives the throttling device made of a nozzle to define varying throttling cross-section.
EFFECT: enhanced precision.
1 cl, 1 dwg
SUBSTANCE: reduction valve comprises housing that is provided with supplying, discharging, and draining passages. The cylindrical slide valve is mounted with a spaced relation to the spring-loaded pusher inside the bore made in the housing to form a face control chamber from the side opposite to the pusher. The chamber is in communication with the draining passage through the longitudinal passage made in the slide valve. The draining passage is connected with the space that is defined by two slide valve collars. The first collar separates the space from the discharging chamber, and the second one separates it from the control chamber and forms the throttling slot between the supplying and discharging passages. The first collar of the slide valve is mounted with a diametrical space of 1.3-1.8 of the diametrical space of the second collar. The first collar is provided with the ring groove that divides it into two cylindrical parts. One of the parts is located from the side of the pusher and is provided with flats uniformly arranged over the periphery.
EFFECT: expanded functional capabilities.
3 cl, 4 dwg
FIELD: valving systems.
SUBSTANCE: hydraulic throttle valve comprises housing with inlet and outlet openings and spring-loaded slide valve. The slide valve is mounted for permitting reciprocation between the space in the zone of the outlet opening and damping dummy space that are coaxial to it and receives the spring-loaded member. The axes of the outlet and inlet openings intersect. The outlet opening is made at a distance from the inlet opening, and it is overlapped by the side of the slide valve in the throttling interval. The housing of the valve and slide valve has passages that connect the dummy space with the space in the zone of the inlet opening or the space in the zone of the ring groove.
EFFECT: enhanced precision of control.
SUBSTANCE: invention is used, primarily, as cold and hot water pressure stabiliser the dwelling house compartment water supply inlets. The device housing incorporates a pressure regulator with a stem with a gate. There is a seal between the gate and the casing, while between the gate and seat arranged in the regulator control space, clearance is formed. The said control space accommodates a spring-loaded diaphragm. The casing inlet branch pipe communicates, via the manifold, filter element and the clearance between the seat and gate, with the manifold outlet space which, in its turn, communicates with the casing outlet branch pipe. The regulator stem is fitted in the outlet space communicating with the control space. The invention allows increasing pressure regulation accuracy thanks to reducing friction of the regulator sealing elements and increasing its operating speed.
EFFECT: higher accuracy and operating speed.
2 cl, 1 dwg
FIELD: machine building.
SUBSTANCE: proposed invention can be used for control purposes in oil refining, chemical processing installations, foodstuffs processing units or similar. Essence of the invention consists in the valve system containing the mechanism moving the valve to its safety position. The system incorporates the valve actuator wherein a fluid medium is forced by the aforesaid controller comprising the pressure relief reversing valve. Note that if pressure in the valve actuator should be reduced for the valve to move into its safety position, the aforesaid reversing valve opens to form a channel to instantaneously drop excess pressure at the controller outlet.
EFFECT: control over pressure and fluid medium flow rate.
22 cl, 3 dwg
FIELD: machine building.
SUBSTANCE: invention relates to gas industry and can be used in gas transportation and use. The proposed two-stage gas pressure reducer is made up of body 1, cover 2 with inlet union 3 and two stage of pressure reduction. Note that the first stage consists of valve 10, first sensitive element with first piston 4 with a con-rod and axial channel 5 arranged therein, axial spring 6 and the following spaces, i.e. first outlet space7, under-piston space 8 and above-piston space 9. The second stage consists of the second sensitive element with second piston 11, screw 12 and pressure setting spring 13, second valve 14 with seat 15 and the following spaces, i.e. second outlet space 16 and pressure setting space 17. Note also that the first stage under-piston space 8 communicates via channel 18 with the second stage second outlet space 16. Note also that filter 19 representing a set of screens is arranged between body 1 and cover 2 with inlet union 3. Second valve 14 represents a ball with push rod 20, its second end being provided with thrust washer 21 with spring 22. The said ball surface 23 is in a point contact second piston 11.
EFFECT: higher reliability.