SU1275393A1 - Gas pressure regulator - Google Patents

Abstract

The invention relates to the field of pneumatic automation and can be used to control the gas pressure in pneumatic systems. The purpose of the invention is to increase accuracy and reliability, control and reduce the time of initial filling of the output chamber. The gas pressure regulator comprises a housing with inlet and outlet chambers, between which a seat and a valve are installed. In the spring-loaded sensing element, a differential piston is installed, which (Connected by a smaller step through a pusher with a valve. The cavity formed by the differential piston and the sensitive element on the side of the larger stage is communicated through the channel with the throttle to the output chamber, and the cavity formed by the differential piston and sensitive element with side of the lower stage, communicated with the atmosphere, while in the initial position of the regulator between the seat and the valve there is a gap in the case of rigid contact Potential piston with a sensing element. A channel with a throttle communicates with a slit intake formed by the sealing surface of the valve and the end surface of a fixed (L associated disk element. Hard connection of the disk element with the valve and the simultaneous displacement of the differential piston with the sensitive element increases accuracy and the reliability of the regulator, as well as shortens the time of the initial filling of vj or the output chamber. 1 il. ate 00 x

Description

The invention relates to pneumatic automation and can be used to regulate gas pressure in pneumatic systems.

The purpose of the invention is to improve the accuracy and reliability of the controller and reduce the time of initial filling of the output chamber,

The drawing shows a gas pressure regulator.

The regulator consists of body 1 with input 2 and output 3 cameras. The sensing element 4 is biased by the adjusting spring 5 and contacts over the surfaces A and B with the differential piston 6 from the side of its larger stage, which through the pusher 7 acts on the valve 8 pressed in the direction of the seat 9 by the spring 10. Differential piston 6 from the side of the greater stage in the sensing element 4 it forms a cavity 11 in communication with the throttle 12, filled in the channel 13, with a slotted intake 14, formed by sealing the surface of the valve 8 and the end surface of the fixedly connected disk of member 15. The cavity 16 is formed in the element 4 chuvstvitelnbm differential piston 6 by its lower stage. Cavities C and D limit the position of the differential piston 6 in the operating mode of the regulator. At this, the relations

Hg

.

: one

Max

de X is the minimum clearance between the valve 8 and the saddle 9 in the initial position of the regulator;

X is the gap between the contact surfaces G and C, the differential piston from the lower stage and the sensitive element, respectively; max maximum clearance Mervdu

valve and seat in the operating mode of the controller

, Uidks,

(vF-P

MII

where, - the maximum force from the valve on the differential piston;

dR - the difference of areas greater) and the lower stages of the differential piston; “Ying minimum regulator outlet pressure.

The pressure regulator operates as follows.

In the initial position of the regulator with a compressed adjusting spring 5, the inlet 2 and outlet 3 of the chamber are communicated with a minimum clearance X. When the working medium is supplied under pressure, it enters the outlet chamber 3 and through the slit intake 14, channel 13 and drole5 sel 12 into the cavity 11. Smallness gap X causes the smoothness of the filling of the output chamber 3 without exceeding the pressure determined by the compression of the adjusting spring 5. At this time, 0 yes. The in-cavity 11 continues to increase and upon reaching a certain value it begins to move the differential over 6 to several press the valve 8 from the saddle 9.

The pressure in the output chamber 3

Somewhat upwards, and when the contact surfaces C and H are in contact, a gap appears between the sensing element 4 and the housing 1, and the pressure in the output chamber 3 is equal to the required tuning pressure.

The difference in the areas of the steps of the differential piston 6 is chosen such that at the minimum output pressure for which the regulator is designed, the force on the piston is not less than the force from valve 8, which folds out of the force of spring 10 and force from the input pressure on the valve. The differential piston 6 and the sensing element 4 become a rigid system and, under conditions of varying gas flow and inlet pressure, move together, providing a clearance between the valve and the seat. The absence in the operating mode of movement of the differential piston 6 relative to the sensing element 4 causes the minimum deformation of the adjusting spring 5 and the reduction of the adjustment error.

If output chamber 3 has

Claims (1)

55 large volume, the time of its initial filling, i.e. the time to reach the minimum output pressure Rdlin of the response pressure of the piston 6 is shortened due to the fact that the pressure in the slit inlet 14 due to the increased density of the medium and the speed of its outflow exceeds the pressure in the outlet chamber 3, i.e. The pressure in cavity 11 reaches the minimum required value for the release of valve 8 earlier than the same pressure will be in the entire volume of the outlet chamber. Despite the increased pressure in the intake 14, the throttle 12 ensures that the valve 8 is depressed at such a rate that the overpressure of the outlet pressure is prevented. The fixed, rigid connection of the disc disc 15 with the valve 8 excludes self-oscillations of the regulator at higher pressures in the intake. A rigid differential piston system - a sensitive element reduces the likelihood of self-oscillations, eliminates friction pairs in the adjustment mode, simplifies the design, which leads to an increase in the reliability and accuracy of the regulator. The use of the proposed regulator allows to increase the accuracy of pressure control in gas supply systems, increase their reliability and reduce costs, as well as reduce the time of initial filling of output lines. The formula of the invention and the gas pressure regulator, comprising a housing with inlet and outlet chambers, between which a regulating body in the form of a seat and a valve is installed, a differential piston installed in a spring-loaded adjusting spring sensing element and connected in a smaller step through a pusher with a spring loaded valve to the control valve, moreover, the cavity formed by the differential piston and sensitive zlement from the side of the greater stage is communicated through the channel with the throttle to the output chamber, and the cavity, forming The differential piston and the sensing element on the side of the lower stage communicate with the atmosphere, while in the initial position of the regulator between the seat and the valve there is a gap when the differential piston is in firm contact with the sensitive element, characterized in that, in order to increase the regulator's accuracy its reliability and reducing the time of the Initial filling of the output chamber, the channel communicates with the slotted intake, formed by the sealing surface of the valve and the end surface of the fixedly connected with the disk element, with i. 1 V) minimum clearance between the valve and the seat in the initial position of the regulator; the gap between the contact surfaces of the differential piston on the side of the lower stage and the sensor element; maximum clearance between the valve and the seat in the operating mode of the regulator. de N maximum force from the valve to the differential piston; the difference of the areas of the larger and smaller stages of the differential- potential piston; minimum regulator outlet pressure. // five