RU2032928C1 - Gas pressure regulator - Google Patents

Abstract

FIELD: pneumatics. SUBSTANCE: pressure regulator has housing 1 with inlet 2 and outlet 3 spaces, seat with sealing surface, valve coupled with spring 12, and sensitive member 7 having an effort governor constructed as a spring 8. The valve is self- adjusted and has the form of a disk. A baffle, provided with the central opening of the seat, is mounted inside housing 1. The bearing surface and through passages are mounted concentrically to the seat opening. Projections of pusher 9 is mounted inside the passages for allowing contact with the valve which is pressed by spring 12 in the direction of the bearing surface. EFFECT: heightened accuracy of regulating. 2 cl, 5 dwg

Description

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

Known valve shutter, consisting of a stem and holder, which is based on the possibility of self-installation on the saddle of the working body. The saddle and the working body have sealing and supporting surfaces. Compensation of the deflection of the saddle in this device is due to the elasticity of the supporting elements on the saddle [1]
The disadvantage of the device in relation to the pressure regulator is the increased force of sealing the seat due to the preliminary deflection of the elastic elements, after which the process of sealing the sealing surfaces begins. At the same time, the accuracy of regulation during the transition from the expenditure mode to the wasteless one decreases.

Known valve shutter, on the working body and the seat of which there are supporting and sealing surfaces. To compensate for deflection of the saddle, the supporting surfaces of the saddle or working body are offset parallel to the sealing surfaces [2]
In addition to the difficulties of obtaining parallel displacement of surfaces of the technological order, there is a functional disadvantage of the device. The resulting maximum displacement of the bearing surfaces, in the case of small deflections of the seat, for example, when operating at low pressures, can reduce the effect of the valve self-installing in the seat, i.e. the displacement will be excessive and the sealing on the sealing surfaces will not be complete, or with increased sealing force. This, as applied to pressure regulators, will reduce the accuracy of regulation when switching from a flow mode to a waste-free one.

Known pressure regulator (prototype), comprising a housing mounted between the inlet and outlet cavities, a seat with a sealing surface and a valve coaxially connected to the spring, pressed against the sealing surface of the seat, a sensing element with a force adjuster [3]
The location of the supporting and sealing surfaces in the same plane in this regulator, even with perfect flatness, causes, in addition to the sealing force of the sealing surface, a significant force on the supporting surfaces in a non-flow mode and, therefore, a significant difference in output pressure when switching from a flow mode to a non-flow mode. The situation is aggravated when deviations from the flatness of the surfaces are such that the sealing surfaces do not contact and there may be a gap between them, or come into contact with low specific pressures, and all the force or the main part of it is distributed over the supporting surfaces. Separation of the inlet and outlet cavities becomes leaky and the outlet pressure will inadmissibly increase, i.e. the accuracy of the outlet pressure control may be insufficient.

 The technical result of the invention to improve the accuracy of the regulator.

≥ 1, где Н максимально возможный зазор между уплотнительными поверхностями клапана и седла при несиловом контакте клапана с опорной поверхностью, а минимальное усилие принято действующим на диаметре D_т при D_o ≥ D_т, и на диаметре D_o при D_o < D_т.
При этом за минимальное усилие Тм принята разность
Т_м Т_к-Т_г, где Т_к усилие на клапане в направлении седла;
Т_г усилие, необходимое для герметичного перекрытия седла.The technical result is achieved in that the valve is self-aligning and has a disk shape. A partition is made in the housing with a central hole in the saddle, concentric to which are located the supporting surface and through channels. The sensing element is connected with a pusher having protrusions mounted in the said through channels with the possibility of contact with the valve, which is pressed towards the supporting surface. The geometric and mechanical parameters of the valve provide with a minimum force T _m on the pusher diameter D _t contacting the valve, or on the contact diameter D _{on the} supporting surface of the valve deflection P, measured on the diameter D _o , expressed by the ratio

≥ 1, where N is the maximum possible gap between the sealing surfaces of the valve and the seat when the valve is in non-force contact with the supporting surface, and the minimum force is assumed to be acting on the diameter D _t at D _o ≥ D _t , and on the diameter D _o at D _o <D _t.
In this case, the difference T
T _m T _to -T _g , where T _{to the} force on the valve in the direction of the seat;
T _{g is the} force required to seal the seat.

 In addition, the pusher is installed in the central recess made in the sensing element, and the valve is connected to the spring through a holder having an articulation to the valve.

 The substantiation of the materiality of the distinctive features is as follows.

 The execution of the valve in the form of a disk element provides its symmetrical deflection, and by changing the thickness and diameter of the disk, taking into account its mechanical properties, it is possible to obtain the desired deflection.

 The execution of the valve self-aligning contributes to its preliminary installation parallel to the supporting surface and the sealing surface of the seat and its further operation within the deflection.

 The central location of the seat with its concentric surface and concentric to it and, therefore, the peripheral location of the supporting surface along with the direction of the valve pressing toward the supporting surface determine the deflection of the valve and its orientation.

Deflection with a minimum force T _{m is} necessary to exclude the force contact of the valve with the supporting surface and guaranteed overlap of the seat in a non-expendable mode.

количественно отражает условие гарантированного перекрытия седла в безрасходном режиме.Ratio

quantitatively reflects the condition of guaranteed overlap of the saddle in a waste-free mode.

седло останется перекрытым в безрасходном режиме и после снятия задающего усилия на чувствительном элементе. При D_o < D_т расчет прогиба П следует проводить в предположении усилия Т_м по диаметру D_o. В этом случае реальный прогиб от усилия толкателя, приложенного по диаметру D_т, будет над контактным диаметром D_o заведомо несколько большим минимально необходимого.The action of the force Tm taken on the diameter D _t when D _o ≥ D _t so that, subject to the ratio

the saddle will remain closed in non-expendable mode even after removal of the driving force on the sensing element. When D _o <D _{t the} calculation of the deflection P should be carried out under the assumption of a force T _m in diameter D _o . In this case, the real deflection due to the force of the pusher applied along the diameter D _t will be above the contact diameter D _{o a} little more than the minimum necessary.

 The protrusions on the pusher and their placement in the channels of the partition allow, retaining the partition in the housing, which has its purpose, to communicate with the sensor element.

 Installing the pusher in the recess on the sensing element increases the advantage of the device by eliminating the friction of the pusher, in contrast to the option of basing the pusher in the housing on a movable landing.

 Swiveling the valve with the pusher is a specific constructive means of making the valve self-aligning. EFFECT: increased accuracy of the regulator is obtained due to the fact that the sealing force of the saddle is stabilized and reduced, which reduces the regulation error during the transition from the expendable mode to the non-expendable one.

 A pilot test showed good tightness of the valve-seat control pair and the possibility of making the seat and bearing surfaces in one piece with the body in its internal cavities, when the possibilities of fine-tuning the seat geometry are limited and when the sealing surface of the seat is worn during operation.

 In FIG. 1 shows a general view of the controller, the initial position; figure 2 elements of the seat, pusher and valve in a waste-free mode of regulation; figure 3 section aa in figure 2; figure 4, the gap H with non-force (without deflection) contact of the valve with the supporting surfaces and under the assumption that the valve is perfectly flat; in FIG. 5 self-adjusting valve when the spring is not loaded on the sensing element and the valve bends, compensating for the gap N.

 The regulator consists of a housing 1 with an input 2 and an output 3 cavities, between which a saddle with a sealing surface I. element 5. The controller contains a valve 6, a sensing element in the form of a piston 7, connected with a force adjuster by a spring 8 and through the pusher 9 and its protrusions 10 installed in the through channels G, with the possibility the contact with the valve 6. The holder 11 is pivotally connected by a conical surface to the valve 6, preloaded by the spring 12 through its central part to the supporting surface K. The valve 6 has a flat surface B, a sealing surface AND seats and a supporting surface K nominally (excluding deformation and non-flatness ) combined into a flat surface B. The annular element 5 has cutouts forming annular protruding elements 13. The pusher 9 is spaced with a recess D and has an axial protrusion 14 with the contact surface J.

 The gas regulator operates as follows.

 In the initial position of the regulator, the spring 8 is not loaded, the protrusions 10 do not exert a force on the valve 6 and, with a possible initial clearance H, under the force of the spring 12, it can deform and contact with the sealing AND and supporting K surfaces, i.e. mount on saddle.

 When the inlet pressure is applied to the inlet cavity 2, the pressure of the valve 6 against the sealing I and the supporting surface K is maintained, and the contact force with the surface And is still sufficient for sealing.

 When the maximum inlet pressure is applied to the inlet cavity 2, the spring 8 is compressed to obtain the required outlet pressure, but the shut-off element at the output of the regulator is closed (zero-flow mode), the pushing force on the valve 6 will be minimal and equal to the force of the spring 12 minus the force from the inlet pressure valve 6 and automatically set the sealing force of the sealing surface I. In this case, the valve will have a deflection P.

 When the shut-off element at the outlet is open and the consumer draws gas through the regulator, the pressure in the outlet cavity 3 decreases somewhat. The piston 7, responding to this decrease, acts through the pusher on the valve 6, the deflection of the valve increases slightly, the sealing force from the surface And is removed and the valve 6 moves from the seat. Through the formed annular gap, the inflow of gas from the inlet cavity 2 compensates for its outflow from the outlet cavity 3, the outlet pressure is automatically maintained constant.

 In an adjustable flow mode, the deflection of valve 6, although somewhat increased, will remain within the limits of elastic deformations and, upon transitioning to a waste-free mode, will again assume the value P.

 Thus, the valve in the non-flow mode, compensating for the deflection of the gap between the sealing surfaces of the valve and the seat, provides reliable overlap of the seat with minimal loss of force during the sealing process, which ultimately increases the accuracy of the regulator.

Claims (2)

1. GAS PRESSURE REGULATOR, comprising a housing, a seat with a sealing surface installed between its inlet and outlet cavities and a valve coaxially connected to the spring, pressed against the seat sealing surface, a sensing element with a force adjuster, characterized in that the valve is self-adjusting and has a disk shape , a partition is made in the body with a central hole of the saddle, concentric to which are the supporting surface and through channels, the sensing element is connected to a pusher having dumb mounted in said through channels with a possibility of contact with a valve which is biased towards the supporting surface, and the geometrical and mechanical parameters of the valve provide with minimal effort T _m at the contact with the valve diameter D _m of the pusher or on the contact diameter D _of the bearing surface deflection P valve, measured on a diameter of D _about , expressed by the ratio

where h is the maximum possible gap between the sealing surfaces of the valve and the seat with non-force contact of the valve with the supporting surface,
and the minimum force is assumed to be acting on the diameter D _t for d _о ≥ D _t and on the diameter D _о for D _о <d _t , while the difference T _to T _g , where T is _the force on the valve in the direction of the seat, is taken as the minimum force T _m , T _{g is the} force required to seal the seat.  2. The regulator according to claim 1, characterized in that the pusher is installed in a central recess made in the sensing element, and the valve is connected to the spring through a holder having an articulation to the valve.

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