RU2707442C1 - Vessel with seal and compensator of radial and axial beats of vessel shaft - Google Patents

Abstract

FIELD: manufacturing technology.

SUBSTANCE: invention relates to vessels with sealing and radial Δr and axial Δa beating of vessel shaft. Vessel consists of fixed vessel 1, shaft 2 of the vessel and supports of vessel shaft motion. Shaft 2 of the vessel is tightly and rigidly connected to the shaft of seal 5, in this case the magnetic liquid seal (MLS), radial and axial beating of the shaft of the vessel through bearings 6 of the MLS and the housing of MLS 4 are eliminated by compensator 7 and are not transmitted to housing 1. Compensator consists of two parts 15 and 16, with n=2 and with k=n+1=3 by three pairs of interfaces: two sphere-sphere 8 and cylinder-cylinder 11, providing kinematic mobility for sphere-sphere due to rotation of surfaces of pairs in radial plane and translational for pair of cylinder-cylinder. When performing said pairs with clearance, additional mobility are formed within the limits of radial and axial for sphere-sphere pairs and turn in radial plane and radial movement for cylinder-cylinder.

EFFECT: reduced dimensions of the compensator, especially along its axis of rotation with considerable increase of compensated radial and axial beats of the vessel shaft.

1 cl, 12 dwg

Description

The present invention relates to vessels with a seal and a compensator for radial and axial beats of the vessel shaft (vessel) under pressure or evacuated with a compensator for radial and axial beats of the vessel shaft (compensator) and can be used in mechanical engineering, nuclear, biological, chemical and electronic industries for sealing rotating shafts of vessels with a high level of radial and axial beats in the places of compaction.

Known vessels with a seal of the rotating shaft of the vessels mechanical seals [Seals and sealing technique: Reference / L.A. Kondakov, A.I. Golubev, V.B. Ovander et al. - M.: Mechanical Engineering, 1986. - 464 p. (p. 288-350)], containing sealing rings, hermetically mated, respectively, with the shaft of the vessel and the vessel body, tightly pressed against each other along the end surfaces with a gap between them equal to zero, movable relative to each other and providing compensation for the radial runout of the vessel shaft due to the radial displacement of one of the sealing rings relative to the other in the radial direction, and the compensation of the axial runout due to the axial deformation of the elastic elements, for example, bellows.

The disadvantages of the device are the fundamental need for friction surfaces of the sealing rings rubbing against each other during rotation of the vessel shaft, at a speed determined by the shaft rotation frequency and the radius of the contact point. This generates a high friction moment and, accordingly, a high level of loss and heating. The disadvantages include the wear of friction surfaces, which requires a fairly frequent replacement of the sealing rings. The presence of wear products of sealing rings limits the scope of mechanical seals in terms of product cleanliness in the vessel.

Vessels in the form of conjugated exhaust pipes with offset compensators are known, for example, [US Patent 5779282, F16L 27/06, Exhaust ball seal], which contain spherical surfaces on the end parts of two parts of the exhaust pipe, with which they are mated, compensation for manufacturing errors and the possibility of displacement of the exhaust pipe relative to the car body due to rotation in a spherical joint in the radial plane with displacements of the outer parts of the car.

Such designs are intended for static compensation of manufacturing errors of the exhaust system elements and structurally do not have rotating elements inside the specified compensator.

A known vessel with a magnetically liquid seal (MF) for sealing the rotating shaft of the vessels [A.S. 892075, F16J 15/40, Magnetic liquid seal]. The vessel contains a stationary body and a movable shaft of the vessel and support the movement of the shaft of the vessel. The shaft of the MFU is made hollow, covering the shaft of the vessel, and the complex of radial and axial gaps between the magnetic circuits filled with magnetic fluid (MF) provides sealing and compensation of the radial and axial beats of the shaft of the vessel, i.e. plays the role of a compensator.

The disadvantage of the design is the complexity of its manufacture and assembly, requiring high precision manufacturing of parts with a limited level of compensation for beats. At the same time, the compensator is connected with the mating surfaces of the vessel shaft and the shaft of the MFU, rotating synchronously without sliding in the tangential direction.

Known vessel with a seal on its rotating shaft. The seal was installed MFU [AC 1227885, F16J 15/40], which contains a floating cup covering the shaft of the vessel, the shaft of the seal and the magnetic system of the MFU and acting as a compensator. In this case, the floating cup is rigidly connected to the magnetic system of the MFU and through bearings with the shaft of the MFU and the shaft of the vessel. During beating of the vessel shaft, they are transmitted to the MFU shaft and through the MFU bearings to the floating cup with a magnetic system. The magnetic system significantly increases the mass of the floating cup, which leads to a sharp increase in vibration loads on the bearings of the MF. Similarly, the compensator is associated with the mating surfaces of the vessel shaft and the shaft of the MFU, rotating synchronously without sliding in the tangential direction

As a prototype adopted a vessel with a compensator for radial and axial beats of the shaft of the vessel [A.S. 1227884, F16J 15/40], comprising a stationary casing and a vessel shaft movable relative to it, vessel shaft support bearings and a seal comprising a seal housing, a seal shaft and a seal shaft movement support relative to the seal housing. As a seal made MJU. The compensator is a block of the intermediate sleeve and the shaft sleeve (compensator) rigidly, motionless and hermetically sealed by bolts, with one end hermetically mating with the vessel shaft sleeve and the other with the MFU bearing, being its support. Landings at the interface are determined by the requirements for bearing landings and on the joints of the stationary joints of the seals with rubber rings. The moment required for rotation of the MF shaft is transmitted from the vessel shaft to the seal shaft through a number of parts, including the intermediate sleeve (compensator). Therefore, the vessel shaft and the MF shaft rotate synchronously. Axial compensation of the beatings of the vessel shaft is carried out due to kinematic mobility in the axial direction of the vessel shaft sleeve. The seal between them provides a rubber ring.

The indicated block compensates for the radial runout of the vessel shaft by selecting gaps only at the seal of the shaft sleeve on the vessel shaft and at the place of installation of the intermediate sleeve in the bearing by selecting the clearance in the bearing and the gaps at the bearing seats. Since these gaps are small, and compensation is carried out only by sampling these gaps, as shown below, a significant length of the compensator in the axial direction is required. This circumstance narrows the range of compensated radial beats of the vessel shaft and leads to an increase in the dimensions of the vessel.

The task of the invention is the expansion of the range of compensation of radial and axial beats of the shafts of sealed vessels while reducing the dimensions of the compensator.

The technical result achieved by this invention is to reduce the dimensions of the compensator, especially along its axis of rotation (length) with a significant increase in the compensated radial and axial beats of the vessel shaft when transmitting the MF shaft to the torque required for its rotation and practically eliminating the effect on the MF shaft of radial and axial loads from the shaft of the vessel. Reducing the axial dimensions of the compensator also reduces the dimensions of the vessel.

и/или плоские - θ_{fi mах} и/или сферические - θ_{si mах}, где 1≤i≤k, в пределах указанных максимально допустимых кинематических подвижностей пар возможны радиальные r_k и осевые а_k перемещения вала сосуда, при этом поверхности сопряжений каждой пары расположены друг относительно друга с зазорами 0≤δ_mi≤δ_{mi mах}, где δ_{mi mах} - максимально допустимые зазоры между поверхностями сопряжения для указанных уплотнительных элементов, обеспечивающими возможность дополнительных подвижностей пар и образуют максимально допустимые подвижности пар за счет изменения зазора - вращательные - θ_Gtimax и/или поступательные -

и/или плоские - θ_Gfimax и/или сферические - θ_Gsimax, в пределах которых возможны дополнительные радиальные r_G и осевые a_G перемещения вала сосуда, при этом в пределах указанных кинематических и дополнительных подвижностей пар суммарные радиальные и осевые перемещения вала сосуда обеспечивают выполнение условийThe technical result is achieved due to the fact that in a vessel with a seal and radial Δr and axial Δ a beats of the vessel shaft (vessel) containing the stationary vessel body, the vessel shaft, the supports of the vessel shaft movement, the vessel shaft seal containing the seal body, the seal shaft and bearings of the movement of the seal shaft relative to the seal body and the compensator for the radial and axial beats of the vessel shaft (compensator), the seal shaft and the compensator are hollow, covering the vessel shaft, while the vessel body and the seal body, and Also, the vessel shaft and the seal shaft are hermetically sealed with the help of sealing elements, and at least one of the indicated joints is movably coupled to each other through the two extreme mating surfaces of the compensator, while the compensator is made of n = 1, 2, 3 ... parts, n-1 parts of which are hermetically and movably mated to each other through these sealing elements, a compensator and two of these movable mating surfaces contains k = n + 1 pairs of mating surfaces (pairs) that are movable relative to each other, at om said surface pairs are formed as surfaces of revolution and / or flat, forming the kinematic couple [Kozhevnikov SN Yesipenko Frenkel, YM Raskin The mechanisms. Directory. - M.: Mechanical Engineering, 1976. - 784 p. (p. 18-36, p. 53-74)], p. 53-74)], having the maximum allowable kinematic mobility of pairs for a given design and vessel geometry: rotational θ _{ti max} and / or translational -

and / or flat - θ _{fi max} and / or spherical - θ _{si max} , where 1≤i≤k, within the specified maximum allowable kinematic mobilities of the pairs, radial r _k and axial a _k movements of the vessel shaft are possible, while the mating surfaces of each pair are arranged relative to each other with gaps 0≤δ _mi ≤δ _{mi max} where δ _{mi max} - maximum allowable clearance between said mating surfaces for sealing elements, providing the possibility of additional pairs of mobility and form pairs of the maximum allowable mobility due measurable eniya gap - rotational - θ _Gtimax and / or translational -

and / or flat - θ _Gfimax and / or spherical - θ _Gsimax , within which additional radial r _G and axial a _G movements of the vessel shaft are possible, while within the specified kinematic and additional mobilities of the pairs, the total radial and axial movements of the vessel shaft provide conditions

and

Variants of location of sealed stationary and movable joints of the compensator between the vessel shaft and the seal shaft and between the vessel body and the seal housing or the simultaneous use of movable mates between these shafts and housings are possible. The compensator can be located below and above, inside and outside of the MF. In all embodiments, the mating surfaces are made in the form of surfaces of revolution and / or flat, that is, for example, be spherical, conical, cylindrical, toroidal and others, determined by the form of the generators and / or flat with any combination of their mates. For example, mating pairs can be formed by the surfaces of a sphere — sphere or sphere — cylinder or plane — plane or plane — toroid or cylinder — cylinder, etc. Numerical values in the form of possible rotation angles, radial and axial displacements depend on the type of mating surfaces in pairs and on the design features of the vessel. The choice of the type of surfaces of the pairs depends on the parameters and geometry of the vessel and the level of permissible radial and axial beats of the shaft of the vessel.

The invention is illustrated by drawings, where shown.

In FIG. 1 is a longitudinal section of a vessel in the area of the MF and the compensator installed between the shaft of the vessel and the seal shaft below the MF.

In FIG. 2, 3, 4 are enlarged images of the structure of FIG. 1 at the locations of the sealing elements. In FIG. 2 version of the fixed and tight connection of the vessel body with the body of the MFU through the compensator. In FIG. 3, 4 variant of tight and movable joints of the compensator with the shaft of the vessel and the shaft of the seal.

In FIG. 5 is a longitudinal section of the vessel in the area of installation of the MF and the compensator installed between the shaft of the vessel and the shaft of the MF inside the MF.

In FIG. 6 shows a longitudinal section of the vessel in the area of the MF and the compensator installed between the vessel body and the MF housing outside the MF.

In FIG. 7 shows a longitudinal section of the vessel in the installation area of the MFU and the expansion joint with a bellows.

In FIG. 8 shows a longitudinal section of the vessel in the area of the MF and compensator with spherical pairs and the designation of the main dimensions.

In FIG. 9 shows a diagram of the vessel of FIG. 8 with the position of the compensator in the initial position and in the position and in the offset position of the vessel shaft.

In FIG. 10 and 11, the position of the pair, with the gap between the interface surfaces of the sphere-sphere in the initial position and the possible radial or axial movement of the shaft of the vessel due to the selection of the gap.

In FIG. 12 shows the arrangement of the mating surfaces on the surfaces of rotation of the cylinder-cylinder in the neutral position and when moving the shaft of the vessel due to the selection of the gap.

In FIG. 1 shows a vessel with a seal and a compensator Δr and axial Δa of the beat of the vessel shaft located between the vessel shaft and the seal shaft. The vessel consists of a fixed vessel body 1, the shaft of the vessel 2 and the supports of the movement of the shaft of the vessel (not shown). As a rule, the pressure inside the vessel is different from atmospheric or (if they are equal), it is necessary to separate the volume of the vessel from the atmosphere for technological reasons or for safety reasons. This leads to the need to install a seal, in which known seals can be used, for example, labyrinth, end, magneto-liquid (MF) and others. In this case, the MFU has been adopted, which makes it possible to fully realize its positive qualities: absolute tightness, low friction moment and loss, and the absence of wear of solids during friction. FFS 3 contains the housing FFS 4, the shaft FFS 5 and the motion bearings (bearings) of the shaft FFS 6. The introduction of the compensator 7 provides greater allowable radial and axial runout of the shaft of the vessel in the absence of collisions of the shaft of the vessel and the shaft of the FFS. The shaft MFU and the compensator are made hollow in the form of bodies of revolution, covering the shaft of the vessel.

The seal of the fixed connection of the vessel body and the housing of the MFU (see Fig. 2) is provided by known sealing means: metal, plastic, rubber gaskets and sealing rings of various sections. In this embodiment, the seal is shown with a rubber ring of circular cross section 8.

The compensator 7 of FIG. 1 hermetically and movably connects the shaft of the vessel and the shaft of the MFU. The mobility of their connection is provided by mating on spherical 9 (see Fig. 3, 4) surfaces. In this case, spherical conjugations provide mutual rotation due to the kinematic mobility of the sphere-sphere in radial and tangential planes and additional mobility in the radial and axial directions within the gap between them. Some of these mobilities, for example, mutual rotation in the tangential direction, can be eliminated by fixing, for example, using a sleeve with spherical liners 10. Within the specified kinematic and additional mobilities of the pairs, the total radial and axial movements of the vessel shaft ensure the fulfillment of conditions (1) and (2).

The compensator of FIG. 1 consists of one part n = 1 and is conjugated in two pairs of sphere-sphere with the shaft of the vessel and the shaft MJU.

For ease of assembly, the spherical surfaces can be made integral, for example, with patch flanges 11 and 12. The joints of the flanges and shaft elements must be sealed by the means indicated above, in this case, rings 13 and 14.

In FIG. 1 pairing points are located inside the vessel, which allows to reduce the dimensions of the vessel as a whole. However, these joints are subject to the action of the product inside the vessel, which requires additional measures for their protection.

In FIG. 5, the shaft of the vessel 2 is hermetically and movably connected to the shaft of the MFU 5, through the compensator 7. The housing 4 of the MFU through the bearings 6 centers the shaft of the MFU and is stationary and hermetically mated with the body of the vessel 1. In contrast to FIG. 1, the compensator is located inside and on top of the MFU, which allows for simple protection from the product (not shown) to significantly reduce or eliminate the occurrence of the specified product in the pair of the compensator in its lower part. The location of the upper pair of the compensator above the MFU simplifies the installation of the MFU and the compensator. At the same time, the location of the compensator inside the MFU increases the radial dimensions of the bore of the MFU shaft by the thickness of the compensator and the gap between the compensator and the MFU shaft, which will inevitably lead to an increase in the external dimensions of the MFU and its mass.

In FIG. 6 radial and axial runout of the shaft of the vessel 2 through the shaft of the MFU 5, the bearings of the MFU 6 and the housing of the MFU 4 are eliminated by the compensator 7 and are not transmitted to the vessel of the vessel 1. In this embodiment, the compensator consists of two parts 15 and 16, i.e. n = 2 with three pairs: two sphere-sphere 8 and cylinder-cylinder 11, providing hermetic kinematic mobilities for the sphere-sphere indicated above, and translational for the cylinder-cylinder pair. When these pairs are executed with a gap, additional mobilities are formed: radial and axial for the sphere-sphere and rotation in radial planes and radial displacements for the cylinder-cylinder pair, which, in combination with kinematic mobilities, fulfill conditions (1) and (2).

To eliminate (reduce) the action of the masses of the housing of the MFU and the compensator on the bearings of the MFU, a spring 17 can be built into the vessel.

This embodiment allows you to remove the compensator from the inner zone of the vessel, thereby eliminating the ingress of the product into the movable mates of the compensator. At the same time, the dimensions and mass of the compensator increase.

In FIG. 7 shows an embodiment of the compensator of FIG. 1 with reduced axial stiffness, for example, by introducing a bellows 18. For n = 1, the compensator ensures that conditions (1) and (2) are satisfied due to the kinematic and additional mobilities of the pairs and due to the elastic deformation of the bellows.

The simultaneous use of the above options for installing compensators when connecting the vessel shaft and the MF shaft and when connecting the vessel body and the MF housing (not shown) allows to reduce the axial dimensions of the compensator, but complicates the design of the sealing assembly and the compensator.

On the longitudinal section of the compensator, coupled with the shafts of the vessel and MFU (see Fig. 8), presents the dimensions that determine its geometry. The shaft of the vessel 2 with a diameter of d is in a neutral position without radial and axial displacements. The location of the compensator 7 between the shaft of the vessel and the shaft of the MFU 5 determines the need for radial gaps between the shaft of the vessel and, accordingly, the inner diameter of the shaft of the MFU Δ _S ≥ Δ _r and between the shaft of the vessel and the inner diameter of the compensator Δ _k ≥ Δ _r. The latter can be variable, increasing from the place of interfacing with the shaft of the vessel 19 to the place of interfacing with the shaft of the MFU 20. The fulfillment of these conditions prevents touching and impacts of the shaft of the vessel on the MFD and the compensator, but requires the internal diameter of the shaft of the MFU and the internal diameter of the compensator , in the field of pair 15, not less

In this case, the pair of mates 19 and 20 are spherical, providing the above mobility. The diameters of the spheres are generally not equal to each other. The distance between their centers is L. The diameters d ₁₁ , d _1N , d ₂₁ , d _2N are the diameters of the location of the sealing elements that determine the allowable clearances between the surfaces of the mating pairs.

The pairing surfaces of the pairs on the expansion joint can be located outside or inside and above or below relative to the MF. For example, in FIG. 9 the surface of the expansion joint pair of the vessel shaft - the expansion joint is located outside the pair, and the pair shaft MJU - expansion joint inside. The generatrix of the compensator between pairs of mates may differ from cylindrical and, for example, be conical, ensuring that its generatrix axis of the vessel shaft is parallel in the plane of the maximum radial displacement of the vessel shaft. Obviously, in this case, for a given center distance between the centers of the pairs (mating centers), the length of the compensator will be minimal.

From a practical point of view, it is most expedient to use kinematic mobility, for example, as shown in FIG. 6, 9, where, to compensate for radial beats, pairs of spherical surfaces forming spherical kinematic mobilities are selected, and to compensate for axial beats of a pair, a cylinder-cylinder pair forming translational mobility is selected. In this case, these pairs can work without changing the gap between the surfaces of the pairs. To satisfy the above, spherical pairs must rotate relative to each other with respect to their common centers lying at a distance L from each other. In this case, with a radial shift Δ _r of the vessel shaft (see Fig. 9), the condition must be satisfied (without taking into account the change in the distance between their centers)

where α is the permissible angle of rotation of the surfaces of the pairs relative to each other in the radial plane, determined by the design parameters of the articulated surfaces. For example, for spherical pairs, the rotation angle in radial planes can reach 5 ^O (the value is determined by the diameters of the sealing elements d ₁₁ , d _1N , d ₂₁ , d _2N and is limited by dynamic loads in spherical pairs and can be increased at low speeds of the vessel shaft). In this case, the distance L in accordance with (3) should be L ≥ 11.5Δ _r , which, for example, at Δ _r = 5 mm will require the fulfillment of the condition L ≥ 57.5 mm.

At the same time, along with the use of kinematic mobilities of the spheres, additional mobilities can be used by changing the gaps between the spheres. The movement of the surfaces of the pairs relative to each other in the radial plane occurs between two limit directions: the movement in the radial and axial directions within two gaps between the two pairs until the two surfaces of the pairs touch. Obviously, the limiting movement of two pairs of compensator in the radial direction is (δ _k + δ _s ) (see Fig. 11) and in the axial direction θ _{Gl max} . (see Fig. 10). Hence, for the structure of FIG. 9, two limiting variants of compensation of the radial and axial beats of the vessel shaft are possible. With a radial selection of gaps δ _{k1 (2)} (see Fig. 10), the limits of radial and axial displacements

and with axial clearance sampling, the limits of radial and axial displacements

Obviously, simultaneous movement along the axial and radial sampling of the gap is possible taking into account the fulfillment of conditions (4) and (5). In this case, the gap between the pairs can be selected in whole or in part, leaving a margin of movement.

In the diagram of FIG. 12 pairs of interfaces are made in the form of cylinder-to-cylinder surfaces of rotation with radial gaps between them δ _k1 and δ _k2 , determined by the conditions for maintaining the tightness of the sealing elements (not shown) between the surfaces of the pairs. The axial runout of the vessel shaft is compensated by the kinematic mobilities of the pairs, which together ensure the fulfillment of condition (2) at a _G = 0. With a radial displacement of the vessel shaft within

there is a radial selection of gaps. Next, the compensator rotates within the specified gaps. The law of movement of the compensator during its rotation is quite complicated and must take into account the totality of forces and moments acting on the compensator through the sealing elements, the geometric dimensions of the compensator and the surfaces of the pairs. In the end, the compensator will rotate an angle

where R _SR is the average radius of rotation of the end edges of the compensator relative to the center of its rotation. In this case, the minimum length of the compensator must satisfy the condition

In accordance with (7), for additional mobilities within the gaps of cylindrical pairs, the angle of their rotation relative to each other is

In this case, the distance between the centers of the cylindrical surfaces of the pairs in accordance with (8) should be

that at Δ _r = 5 mm requires L ≥ 860 mm.

Therefore, the length of the compensator, and, consequently, its dimensions when using kinematic spherical mobility (see 3a) is more than an order of magnitude shorter than when using additional mobilities due to gaps in cylindrical pairs (see 8a).

Thus, for the whole set of pairs defined by the indicated surfaces of revolution and / or flat surfaces, pairs with kinematic mobility and / or pairs with mobility can be formed due to sampling the gap between the surfaces of the pairs. The choice of a pair is determined by the design of the vessel in the compensator zone, as well as the given levels of radial and axial beats of the vessel shaft. Obviously, with a high level of given radial and axial beats of the vessel shaft, the choice of pairs providing kinematic mobilities is preferable than pairs with mobilities due to sampling of the gap. At small levels of these beats, conditions (1) and (2) can be fulfilled due to the combination of kinematic and additional mobilities of the pairs or solely due to additional mobilities due to the selection of gaps.

For example, with minor radial run-outs of the vessel shaft and with significant axial run-outs, the compensator design of FIG. 12 with cylindrical pairs. They are easier to manufacture than, for example, spherical pairs and, accordingly, cheaper and for small radial run-outs of the vessel shaft, a cylindrical shape of the pairs may be preferable. In any case, conditions (1) and (2) must be satisfied.

The compensator may consist of several parts, as shown in FIG. 6. This allows you to compensate for radial and axial runout of the vessel shaft practically due to kinematic mobility.

It should be noted that the elements of the compaction of the surfaces of the pairs of the compensator when making compensating movements work in the compaction mode of a fixed type, and their relative movements relative to each other relate to periodic movements of the pairs when compensating for beats, vibrations, etc. As an example, consider a pair of flat surface - flat surface perpendicular to the axis of rotation. With the location of the sealing element of this pair on a diameter of 100 mm and with the number of revolutions of the vessel shaft 1000 rpm relative to the second flat stationary surface of the pair, the peripheral speed of the point on the moving plane will be equal to 5.23 m / s (similarly, this is the speed of the relative movement of the end surfaces seals on a given diameter). If the indicated flat surfaces of the pair are located on the compensator and on one of the shafts (vessel or seal) they rotate synchronously, and their movement relative to each other is determined by a given radial runout. With the value of the radial runout of the vessel shaft Δr = 5 mm with the specified geometry and parameters, the radial velocity of the relative motion of the surfaces of the pair for one revolution of the vessel shaft is 0.0055 m / s, i.e. more than three orders of magnitude less than the above. The axial and tangential components of the velocity are equal to zero.

Claims (1)

A vessel with a seal and a compensator for the radial Δr and axial Δа of the beats of the vessel shaft, containing the stationary vessel body, the vessel shaft, support for the movement of the vessel shaft, the seal of the vessel shaft, containing the seal body, the seal shaft and support for the movement of the seal shaft and the radial and axial beats of the vessel shaft , the seal shaft and the compensator are hollow, covering the vessel shaft, while the vessel body and the seal body, as well as the vessel shaft and the seal shaft are hermetically sealed with the help of sealing elements, and, according to at least one of these compounds is movably coupled to each other through the two extreme mating surfaces of the compensator, characterized in that the compensator is made up of n = 1, 2, 3 ... parts, n-1 parts of which are hermetically and movably mated to each other through said sealing elements , the compensator and the two indicated movable mating surfaces contain k = n + 1 pairs of mating surfaces movable relative to each other, while the indicated pair surfaces are made in the form of surfaces of revolution and / or flat, forming a kinema of sul pair having the maximum allowable kinematic pairs of mobility for the design and geometry of the vessel: the rotational θ _{ti max,} and / or translational -

, and / or flat - θ _fimax , and / or spherical - θ _{si max} , where i = 1, ... k, within the specified maximum allowable kinematic mobilities of the pairs, radial r _k and axial a _k movements of the vessel shaft are possible, while the mating surfaces of each pair are located relative to each other with gaps 0 ≤ δ _mi ≤ δ _{mi max} , where δ _{mi max} are the maximum allowable gaps between the pairs for the specified sealing elements, which provide the possibility of additional mobility of the pairs and form the maximum allowable mobility of the pairs by changing the gap - rotation stative - θ _{Gti max} , and / or progressive -

, and / or flat - θ _Gfimax , and / or spherical - θ _Gsimax , within which additional radial r _G and axial a _G movements of the shaft are possible, while within the specified kinematic and additional mobilities of the pairs, the total radial and axial displacements of the vessel shaft ensure the fulfillment of the conditions r _s = (r _k + r _G ) ≥Δ _r and a _s = (a _k + a _G ) ≥Δ _a .

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