RU2308626C2 - Sealing ring for movable and fixed joints - Google Patents

Abstract

FIELD: mechanical engineering; seals.

SUBSTANCE: invention can be used in movable and fixed joints in hydraulic and pneumatic devices as piston rings and as rings for forming shells of sliding bearings. Cross section of sealing ring is essentially two tetragons arranged symmetrically relative to ring axis and forming hollow truncated cone, section of cone wall being formed by four sides. Two sides are parallel to each other and to axis of ring, and one of remaining (third) side is arranged at angle of 0°<α<90° relative to first two sides, and second of remaining (fourth) side is arranged at angle of 0°<α>90° to first two sides. At α=β, section of wall of truncated cone is parallelogram. Section of wall of cone has acute-angle sealing edges found on ends of large diagonal of section, and obtuse-angle edges found on ends of small diagonal of section. All edges are sharp, rounded off or provided with faces. Sealing ring is made of elastically deformable material.

EFFECT: improved reliability of sealing of movable and fixed joints.

7 dwg

Description

The invention relates to a sealing technique and can be used for movable and fixed joints in hydraulic and pneumatic devices as piston rings, as well as rings for forming bearing shells.

Known O-rings of circular cross-section (see GOST 9833-73. Rubber sealing rings of circular cross-section for hydraulic and pneumatic devices. Design and dimensions.).

A significant drawback of O-rings is the tendency to twist when assembling the rings to the place of use, which leads to damage to the rings and loss of tightness of the sealing surface due to a decrease in the contact strip. For reliable sealing of hydraulic and pneumatic devices, a sufficiently wide contact strip of the sealing ring is required. This is achieved by creating an interference fit when installing the ring in the gap between the sealing surfaces, by compressing the ring in the gap, since the gap is smaller than the diameter of the ring section. The width of the abutment band of the O-ring in the deformed state in the gap is approximately equal to the radius of the cross-section of the ring in the undeformed state, i.e. the tightness of the O-ring is in the range from 13% (for large rings) to 40% (for small rings) of the diameter of the ring according to Tables GOST 9833-73. When using such a ring, a great effort is required to move it, due to the large friction on the sealing surface, which leads to a large wear of the ring. Therefore, such rings are used mainly in devices with reciprocating motion and less in devices with rotational motion. A significant drawback of O-rings is the tendency to twist under the action of friction, leading to a loss of tightness and damage to the rings, increasing with an increase in their diameters, and also depending on pressure and other parameters, therefore it is advisable to use them only under light conditions.

O-rings of round, oval, x-shaped and other sections are also known for reciprocating devices, such as compressor rods, valves, etc. (“Seals and sealing equipment.” The reference book is under the general editorship of A.I. Golubev and L. A. Kondakova, M., “Mechanical Engineering”, 1986, p. 160-161, Fig. 4.12).

The disadvantage of rings of round, oval, x-shaped and other sections is the low resource of the rings, caused by their wear due to the large interference in the sealing gap. The specified interference is maintained due to the intrinsic elasticity of the rings, which quickly decreases due to wear and tear, as well as due to the aging of the material of the rings.

Known piston rings of internal combustion engines of metals, plastics, carbon graphites or composite materials, which are split to ensure that the rings are pressed against the cylinder wall due to the spring properties of the rings ("Seals and sealing equipment". Reference book under the general editorship of A.I. Golubev and L.A. Kondakova, M., “Engineering, 1986, p. 175-176, Fig. 4.22).

The main disadvantage of these rings is their low tightness, forcing to install from two to six rings on the piston.

Known liners and bushings of sliding bearings having devices for adjusting the clearance in bearings (P.I. Orlov "Fundamentals of Design", Reference and Methodological Manual. Book 2. M., "Engineering", 1977, p.400-401 Fig. 388-390).

The disadvantage of these liners and devices for regulating the gap is the uneven wear of the liners. The cylindrical shape of the bearing hole is violated, the hole becomes oval, which cannot be corrected by tightening the bearing cap. Moreover, the range of regulation of the gap is very small.

The closest analogue (prototype) to the present invention is a sealing ring made of elastic material (see "A sealing ring made of elastic material and a mold for its manufacture", RF patent No. 2249136, IPC F16J 15/00, prior dated 10.17.2002, ., published March 27, 2005).

A disadvantage of the known ring design is its shape, i.e. the cross section of the ring, resulting in the operation of the devices, as a result of the occurrence of pressure of the medium and the asymmetry of the support of the ring on the wall of the groove, to insufficient torque turning the ring around its center. In this case, the maximum shoulder size of the application of force on the pressure of the medium on the ring is equal to half the inner diameter of the ring, i.e. half the size of the cross section of the ring, and the reference turning point of the cross section is at the projection point of the center of the cross section of the ring on the supporting wall of the groove. Thus, the sealing ability of the ring is not fully utilized.

The task of the invention is to increase the reliability of the seal of movable and fixed joints and expand the field of use of the inventive sealing ring for movable and fixed joints.

The problem is solved due to the fact that the sealing ring for movable and fixed joints, the cross section of which is two quadrangles symmetrically located relative to the axis of the ring, which form a hollow truncated cone, the wall section of which is formed by four sides, two of which are parallel to each other and the axis of the ring, one of the remaining sides (third side) is located to the first two at an angle of 0 ° <α <90 ° and the second of the remaining sides (fourth side) is located to the first two the mind is also at an angle of 0 ° <β <90 ° and for α = β, the section of the wall of the truncated cone is a parallelogram, and the section of the wall of the cone has acute-angle sealing lips located at the ends of a large diagonal section and obtuse-angled edges located at the ends of a small diagonal section In addition, all the edges can be made sharp, rounded or chamfered, while the material from which the sealing ring is made must be elastically deformable.

The technical result is achieved by performing a cross section of the ring in the form of a hollow truncated cone, the wall section of which is formed by four sides, two of which are parallel to each other and the axis of the ring, and the other two sides are located to the first at angles of 0 ° -90 °, and the material from which the sealing ring is made - elastically deformable.

The invention is illustrated by drawings, where: Fig. 1 shows an example of a sealing ring for movable and fixed joints, in section; figure 2 is a drawing of a set of rings for sealing the compressor rod, section; figure 3 is a drawing of the piston rings in the internal combustion engine, section; figure 4 is an enlarged drawing in a circle 1 in figure 3; figure 5 is a set of rings forming a bearing shell, section; Fig.6 is a section along aa of the bearing of Fig.5; 7 is an example of a specific implementation of the sealing ring.

In figure 1, the sealing ring 1 with the axis 2 is a sectional view of a truncated cone 3 formed by two quadrangles that are mirrored relative to the axis of the ring 2. Two sides of the ring 1 - 4 and 5 are parallel to its axis 2, and sides 6 and 7 are located at angles α and β equal to 0 ° -90 °. Figure 1 shows a special case when α = β, i.e. the section of ring 1 is a parallelogram, in which 8 and 9 are sealing lips, 10 is the large diagonal of the parallelogram, 11 and 12 are obtuse-angled edges, 13 is the small diagonal of the section, and 14 is the center of the section of the ring 1.

In Fig.2 shows a sealing rod of the compressor, including position 1-12, as in Fig.1, as well as packing follower 15, a ring for supplying lubricant 16, large 17 and small 18 oil pockets and 19 - rod. In addition, the acute-angled edges of the ring 1 are made with chamfers 20.

Figure 3 shows a drawing of the piston rings in the internal combustion engine, which shows the sealing ring 1 with axis 2, the inner d and outer D diameters of the ring, as well as the supporting walls of the groove 21 and the piston 22, and the region 1, which is enlarged in figure 4, is highlighted, where: the enlarged ring of ICE 1, its parallel sides 4 and 5, the angles α and β, and the center of the section of the ring 14.

The set of rings that form the bearing shell (see Fig. 5) includes positions 1 — the sealing ring, 14 — the center of the section of the ring 1, angles α and β, 15 — the groove-book, 17 and 18 — oil pockets, and 23 — the shaft, and inner d and outer D ring diameters.

Figure 6 shows a section along aa of the bearing of figure 5, which shows the location of the oil pockets 18.

In Fig.7 shows the inventive ring, sealing elasto-deformable, for example rubber. The positions indicated are ring 1, its axis 2, which coincides with the axis of the cylinder-piston pair being sealed, parallel sides 4 and 5, as well as 6 and 7, angles α and β, and they are equal in this case, the cone 3 of the ring section, the inner d and outer D diameters of the ring, and also a pair of forces F. The section of the wall of the ring 1 is located at an angle of 90 ° - α to the supporting wall 24 of the groove 25 of the piston 26. The pressure of the medium enters the groove 25 from the side of its end 27. Under the action of pressure a sealed medium produces a torque, i.e. a pair of forces F applied to the shoulder. The shoulder size is D-d / 2, where - D is the outer diameter of the ring, and d is the inner diameter of the ring (Fig. 7).

Consider the operation of a pair of cylinder-piston shown in Fig.7. Under the action of the indicated pair of forces, the ring 1 rotates around the center of the cross section of the ring 14 and the large diagonal of the cross section 10 tends to stand at a distance across the groove 25, thereby increasing the sealing ability of the inventive sealing elastically deformable ring.

When sealing, for example, moving reciprocating compressor rods, a set of the claimed sealing rings is used (FIG. 2). Ring 1 is used to supply lubricant to the large oil pockets 17 between the rings 1, and then to the small oil pockets 18. Under the action of the pressure of the medium being sealed or under the pressure of the packing follower 15, the ring 1 rotates around the centers of their section 14, increasing the sealing ability of the rings and, at the same time, reducing the total contact area of the rings to the rod 19 and the cylinder and thereby reducing the force required to move the rod 19. After reducing the pressure of the medium, the rings 1 under the action of the forces of their own elasticity return to their original position while tightness is maintained by increasing the area of contact of the rings 1 to the rod 19 and the cylinder.

In figure 3 and 4, the inventive ring 1 can be used as a piston ring for internal combustion engines, reciprocating compressors, vacuum pumps, etc. Ring 1 is made not split, but in the form of a hollow truncated cone, the wall section of which has two sides 4 and 5 parallel to each other and the axis 2 of the piston ring 1 22. With increasing pressure of the medium, for example, a flammable gas, the ring 1 rotates relative to the center 2 and provides reliable locking (sealing) of the combustion chamber, which increases the efficiency of the engine and does not require the use of several o-rings. Ring 1 can be mounted in the piston groove by heating it or using a composite piston.

5 and 6, the inventive ring 1 can be used in the form of a set of rings to create a plain bearing shell for a rotating shaft 23. In addition to the extreme rings, the set rings have semicircular grooves 18 on their inner surface, creating an oil wedge in the bearing. The oil enters through the shaft openings into the oil pocket 17 between the middle rings, and then into the indicated grooves 18. The rings in the set are subjected to axial compression by packing follower 15 or environmental pressure (if any). The extreme rings 1 in this case serve to seal and hold the grease in the bearing.

Thus, the advantages of the claimed invention are to increase the reliability of compaction of movable and fixed joints by making the ring of elastically deformable material of the claimed cross section, because the maximum shoulder size of the application of force F from the pressure of the medium on the ring is D-d / 2, and not d / 2 as in the prototype, i.e. the pivot point of rotation of the cross section of the ring is located in the center of its cross section and the ring rises to a distance across the sealing surface, increasing the reliability of the seal.

The inventive sealing ring covers the entire scope of the sealing rings of round, oval, x-shaped and other sections, but has significant advantages when used, i.e. provides high tightness of the sealed surface, thus, is more versatile and high-quality.

The use of the claimed sealing rings covers other areas of use, including the sealing of the rods of compressors and gate valves, rings in the internal combustion engine, plain bearings, etc.

The advantages of the claimed invention are to increase the reliability of the seal of movable and fixed joints by making the ring of elastically deformable materials and the claimed cross section, as well as to expand the field of use of the inventive sealing ring for movable and fixed joints.

Claims (1)

O-ring for movable and fixed joints, the cross section of which is two quadrangles symmetrically located relative to the axis of the ring, characterized in that the section of the ring forms a hollow truncated cone, the wall section of which is formed by four sides, two of which are parallel to each other and the axis of the ring , one of the remaining sides (third side) is located to the first two at an angle of 0 ° <α <90 °, and the second of the remaining sides (fourth side) is also located at an angle 0 ° <β <90 °, and for α = β the section of the wall of the truncated cone is a parallelogram, and the section of the wall of the cone has acute-angle sealing lips located at the ends of the large diagonal of the section and obtuse-angled edges located at the ends of the small diagonal of the section, the sealing lips are sharp, rounded or chamfered, and the sealing ring is made of an elastically deformable material.

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