RU2003906C1 - Ball valve seat - Google Patents

Description

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(glH819742 / 29

(22) 04/27/90

{46) 30.1193 Bud # 43-44

(71) North Caucasian State Scientific and Production Institute of Petroleum

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(7E Varlamov- {1.04 Tipugin A8 .; Protasov V.N; DolozaE .G, (73) North Caucasian State Scientific and Design Petroleum Research and Design Institute

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4) BALL VALVE SEAT

(57) Usage: to shut off the flow of kidcoi or gas. SUMMARY OF THE INVENTION; an elastic yii-solid ring is laid in a trapezoidal groove with a supporting surface at the base and lateral and internal locking surfaces. (made in the form of Parallel Gkogrash, the two intersecting sides of which are connected with the inner castle and supporting along the grooves. The side of the parallelogram, which is lapel. of the supporting surface, is equal to the minimum distance between the outer and inner surfaces of the groove. 8 ill.

The invention relates to ball valve means for shutting off a fluid or gas flow and, in particular, can be used in valve systems of test equipment (test reservoirs, samplers, safety valves, wellhead equipment, etc.).

A ball valve is known comprising a seat housing, a bore, and a sealing surface in which the seal is provided by ground metal surfaces of a sphere and a gray, and the latter is made of softer metal than a ball (US Patent No. 3,814,182, CL 166- 266 dated 4.06.74),

A disadvantage of this design is the low life of the saddle when operating in a liquid or gas environment with abrasive particles, the need to replace the entire valve ball assembly and two seats when one of the sealing surfaces is damaged, and also the great laboriousness of manufacturing.

The closest and accepted for the prototype is a ball valve seat containing a housing with a bore and a seal made in the form of an elastic sealing ring located e trapezoidal groove with a supporting surface in the base and lateral outer and inner locking surfaces (French patent No. 2527730 Cl F 16K5 / 06, 1983).

Its disadvantages include a limitation on performance in an environment whose temperature exceeds 150,200 ° C. Under the influence of high temperature, the rubber o-ring is destroyed and the saddle needs to be replaced after each operation. In addition, during prolonged storage, the rubber sticks to the metal surface of the ball.

The aim of the invention is to improve performance at high pressure and temperature drops.

The goal is achieved in that the known ball valve seat, holding the body with a passage channel and a seal made in the form of an elastic sealing ring located in the trapezoidal groove with a supporting surface at the base and lateral outer and inner eumco surfaces, is improved in that the sealing ring is made in the form of a parallelogram, the two intersecting sides of which are interfaced with the inner locking and supporting surfaces of the groove, and the side of the parallelogram is parallel to the supporting erhnosti, equal to the minimum distance between the outer and inner surfaces of the locking groove.

The completeness of the filling of the grooves is provided only by the shape of the PTFE sealing ring, represented in cross section by a parallelogram with a certain orientation of the sides. The ring will ensure full filling of the groove volume with

the formation of the second castle and supporting P0 surfaces and the formation of the sealing surface of the ring ..

In FIG. 1 shows a saddle assembly; in FIG. 2 shows a saddle body in section; on the

FIG. 3 shows a sectional elastic sealing ring; Ia: Fig, 4 shows the location of the elastic sealing ring in the trapezoidal groove of the housing at the beginning of the assembly; in FIG. 5 - the same, at the end of the press fitting with a spherical punch; FIG. 6 shows a seat with a ball valve in the design of the surface tester; in FIG. 7 - the same, when lowering into the well under the influence of a differential, we press; Fig. 8 is the same during an open test period.

The ball valve seat consists of a steel casing 1, in which there is a passage channel 2 and a spherical surface 3, the radius of which corresponds to the radius of the ball valve Yash.k. (Fig. 2). An annular groove 4 is made on the spherical surface 3, the cross section of which has the form of an isosceles trapezoid ABCD

with aircraft and AD bases. The base of the aircraft forms the supporting surface of the annular groove with dimensions; dc is the diameter of the groove along the top C; do is the diameter of the groove along the top of B.

The sides A. B and CD form the inner and outer castle surfaces. The parties BC and AB form the ABC equal to 40-65. the value of which depends on the elasto-elastic properties of the polymer

(ability 11 to deform without breaking) and the amount of holding force.

The small base of the trapezoid AD forms the open part of the groove with dimensions; do the diameter of the open part of the groove along the top D; dA is the diameter of the open part of the groove along the top A.

On the spherical surface 3, the open portion of the groove AD is 0.33-0.37

the length of this spherical surface, is located symmetrically in the middle of the spherical surface 3.

surface, equal to the minimum distance between the outer and inner locking surfaces of the groove. From Orona KL is located below the LKP to the horizontal. The KN side is located at an angle NKQ of 30-55 ° to the horizontal.

The vertices of the parallelogram form the diameters: dM is the insert diameter at the vertex M; dt is the insert diameter at the vertex L; dN is the insert diameter at the vertex N; dK insert diameter at the top K.

The distance between the sides KL m MN is equal to the distance AD of the groove 4 in FIG. 2.

The sealing elastic ring is made of an elastoplastic material, for example, fluoroplastic, we beat the sealing elastic ring by 1, times the volume of the trapezoidal groove. The angle KLM of the sealing ring of the elastic ring is equal to the angles ABC and BCD of the trapezoidal groove 4.

The dimensions of the seat 1 and the sealing elastic ring 5 are shown in the table as an example of a valve with a ball diameter of 6 with a radius of R 85 mm. An assembly seal ring is inserted into the annular groove 4, as shown in FIG. 4. In this case, the two intersecting sides of the sealing ring 5 ML and LK are conjugated with the inner locking surface BA and the supporting surface BC of the groove 4.

The assembled seat is shown in FIG. 1, where the elastic O-ring 5 is pressed by the punch 7 into the groove 4 with a force exceeding the maximum possible load on the saddle by 20-26% during its operation.

The elastic sealing ring 5 took the form of a trapezoidal groove and protrudes 0.2-0.4 mm above the spherical surface 3 of the seat 1, the saddle is installed in the inlet valve in the formation tester. During preparation of the latter for operation, when there is no pressure drop across the ball valve, the seat 1 is contacted by the ball 6 only along the sealing surface KN of the elastic ring 5 (Fig. 6). This interaction ensures tightness of the joint at the initial stage of lowering the formation tester into the well. ;

Subsequently, as the depth increases, the pressure drop on jape increases, determined by the difference between the hydrostatic pressure of the WG in the well and the pipe pressure Ptr in the drill pipes. The axial force increases, compressing the ball 6 to the seat 1. Under the influence of this force, the elastic ring 5 is deformed and the ball 6 contacts additional HP with a spherical surface 3 (Fig. 7). In this way,

provides a combined seal of the seat 1 with the ball b when lowering the reservoir exploiter into the well.

Once the packer installation test interval has been reached under compressive load, the formation tester's check valve opens. For this, the ball valve is rotated 90 ° so that the axial channel 7 of the ball b is aligned with the axial bore 2 of the seat 1. A pressure equal to the current pressure in the drill pipe is set on both sides of the ball b. Due to the equality of pressure, the axial force pressing the ball disappears. 6 to saddle 1.

The sealing surface KN of the elastic ring 5 under the action of elastic forces again protrudes 0.2-0.4 mm above the spherical surface 3 of the seat 1 (f11g. 8).

At the end of the open period, the formation tester's intake valve closes, i.e. The ball valve returns to its original position. As the ball rotates, the protruding sealing surface KNynpyroro of the ring 5 cleans the ball 6 and traps the abrasive particles. This reduces the wear of the ball b and the spherical surface 3 of the seat 1.

The exchange of open and closed positions of the ball can be made multiple times ..

If the seal on the e-surface KN of the elastic ring 5 is worn or damaged, the latter can be removed from the groove and replaced with a new one as described above.

The practice of working with tubular formation testers shows that the ball valve seat of the proposed design is capable of operating at pressures up to 75 MPa. pressure limitation is associated with the strength of the parts of the drive part of the ball valve and the body of the tester, and the seams.

The use of the claimed proposal makes it possible to increase the life expectancy of the ball valve of the ball type of the formation tester by 1.3-1.5 times by reducing the abrasive wear of the spherical surfaces of the seat and ball; increase by 23-27% the number of successful well testing operations by increasing the reliability of sealing by using a combined seal of the receiving valve of the formation tester; reduce the complexity of manufacturing a ball valve seat by eliminating the need to cut a threaded joint. (56) French Patent fSb 2527750.cl. F 16K 5/06, 1983.

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FORMULA AND 3 REVIEW

BALL VALVE SEAT, made in the form of an elastic sealing ring located in a trapezoidal groove with a supporting surface at the base and lateral outer and inner locking surfaces, characterized in that the tightened ring is made in the form of a parallelogram, the two intersecting sides of which are connected to the inner the locking and supporting surfaces of the groove, and the side of the parallelogram parallel to the supporting surface is equal to the minimum distance between the outer and inner locking surfaces Mi grooves.

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