Gas turbine engine

FIELD: engines and pumps.

SUBSTANCE: first cup-like journal of the first magnetic bearing assembly directed by its bottom to turbine wheel is fitted on engine cylindrical bush adjoining the turbine wheel. Note here that second cup-like journal of the second radial thrust magnetic bearing directed with its bottom to compressor wheel is fitted on the shaft free end. First and second thrust gas bearings, centrifugal compressor wheel and equaliser washer are fitted thereon and locked by nut. Every radial magnetic bearing comprises thin-wall sleeve made of nonmagnetic material. Sleeve outer surface has poles arranged regularly in circle and shaped to trapezoid-like strips made of material with high magnetic permeability. Trapezoid-like strips made of magnetic material arranged between the latter to contact with said poles by side faces. The latter magnetised over axial length in tangentially opposite direction. Wide cross-section base of magnetic strips face the thin-wall surface. Wedges made of strips of nonmagnetic materials are arranged on narrow base side rigidly secured flush with side faces of the poles. Said wedges contact with magnetic strip to make the cylindrical surface extending in working clearance of radial magnetic bearing. Circular ledges of the first and second cup-like journals are fitted in circular recesses. Said ledges are furnished with ring of high-strength fibre on binder made of solidifying synthetic resin. Said ledges are fitted in appropriate ring grooves made in spacer arranged between turbine and compressor casings. Note here that one of ring grooves is opened to compressor while another to turbine. Corrugated sleeve with lengthwise crimps is arranged between the surface of ring grooves and made of resilient material. Inner surfaces of cup-like journal is coated with copper layer and finished to high purity. Thrust magnetic bearing comprises toe bearing made of nonmagnetic material and arranged in cylindrical bore of cup-like journal. Sectors of poles of material with high magnetic permeability are secured between journal bottom and toe bearing surface. Sectors of permanent magnets and sectors of poles are composed by trapezoidal-section strips in contact by side edges. Note here that magnetic sectors face the cylindrical recess bottom by their section wide base. Their narrow bases are covered by flat wedges of nonmagnetic material. Their end surfaces are rigidly secured with end surfaces of appropriate poles to make flat surface which makes with cup-journal the working clearance of thrust magnetic bearing. Radial and thrust magnetic bearings are made of magnetic material with Courier point not lower than 900°C. Elastic washer made of resilient material deformed to make circular crimps is arranged between toe bearing and bottom of bore of both magnetic bearings. Magnetic radial and thrust bearings are locked in place. Axial gas-dynamic bearing comprises spacer and seal with spacer ring arranged there between. Note that first and second thrust gas bearings separated by common toe bearing are fitted there between. Radial gas-dynamic bearing is arranged in clearance between the spacer cylindrical cavity and sleeve surface facing the latter.

EFFECT: reliable starting at low temperatures, higher reliability at high dynamic loads and operating efficiency.

2 cl, 6 dwg

 

The invention relates to the field of turbine construction and can be used when designing, for example, gas turbine engines, turbo compressors, turbo-expanders.

Known gas turbine engine containing the compressor and axial turbine oil cavity between them, in which are the bearings of the compressor and turbine [Schwartz, VA Design of gas turbine plants. M: mechanical engineering, 1970, str, RES].

The disadvantage of this design is its low reliability due to the increased heat transfer in the oil cavity, which leads to overheating and carbonization of the oil and damage the bearings.

Known gas turbine engine, a compressor which includes a housing holds several rows of vanes, the rotor comprising a shell mounted on it a few rows of rotor blades. Two steel caps close the sides of the rotor with the ends and have studs that secure the rotor is supported by bearings. To reduce the axial force to the front end wall of the rotor of the turbomachine of the cavity of the compressor discharge the supplied compressed air. To reduce air leakage from the discharge chamber, it provide two seals placed on the periphery of the axle of the compressor (see Skubachevskii G.S. Aviation gas turbine engines. Design and calculation details. M:Machinery, 1969, Dr.2.14).

A disadvantage of the known device is that you must install seals on the outer and inner surfaces of the gas chamber, through which the leakage of the working fluid GTE.

Also known gas turbine engine, comprising a housing, a cylindrical cavity which has a rotor with a cylindrical outer surface, comprising a shaft, one end of which is rigidly fastened to the impeller of the turbine, which is mounted the rotor bushing made with the possibility of its gas maintenance, and at the free end of the fixed wheel of a centrifugal compressor provided with a thrust bearing (see EN 2456482, IPC F04D 29/051; F01D 3/04, 2012).

When used in the transport of gas turbine engines (GTE) bearings with oil lubrication system lubrication of the bearings, which complicates the installation, increases operating costs, makes the engine run at low temperatures. Use petal gas-dynamic bearings is limited by the mass of the rotors up to 10 kg

The challenge which seeks the proposed solution is to increase the carrying capacity radial and thrust bearing assemblies GTE, improving the reliability of their operation at high dynamic loads, reduction of friction losses in the operating mode, the claim shall Uchenie contamination of the working fluid of the turbomachine oil, increase mechanical efficiency of the CCD.

The result of the proposed technical solutions which seeks to ensure high load bearing capacity radial and thrust bearing assemblies in the working mode, when the reduction of friction losses, reliable running of the CCD at low temperatures, increasing its reliability under high dynamic loads, as well as increase the stability of the rotor to the "half rate vortex, increasing the mechanical efficiency of the CCD.

The problem is solved in that the gas turbine engine, comprising a housing, a cylindrical cavity which has a rotor with a cylindrical outer surface, comprising a shaft, one end of which is rigidly fastened to the impeller of the turbine, which is mounted the rotor bushing made with the possibility of its gas maintenance, and at the free end of the fixed wheel of a centrifugal compressor provided with a thrust bearing, characterized in that the cylindrical sleeve from the side adjacent to the turbine wheel, put the first Cup-shaped pin-heel first thrust magnetic bearing, oriented with its bottom to the turbine wheel, the free end of the shaft has been consistently found to focusing on each other, the second Cup-shaped pin-heel of the second thrust magnetic bearing, the PR is Antonovna its bottom to the compressor wheel, the first and second thrust petal gas bearings, centrifugal compressor wheel and the balancer washer, fixed nut, with each radial magnetic bearing includes a thin-walled sleeve made of nonmagnetic material, on the outer surface of which is uniformly on its circumference are poles, made in the form of bars of trapezoidal cross-section, of a material with high magnetic permeability, between which is placed in contact with the poles of the lateral faces of the magnetic strips of trapezoidal cross-section of magnetic material, on which the entire axial length of magnetized in opposite tangential direction, the magnetic strips broad base of its section facing surface thin-walled sleeve, and by their narrow grounds placed wedges, designed in the form of strips of non-magnetic material rigidly and flush bonded with the side edges of the poles in contact with the corresponding magnetic strip, forming a cylindrical surface facing in the working gap of the radial magnetic bearing, in addition, the annular protrusions of the first and second Cup-shaped pins-toe components of the radial magnetic bearings, equipped with a brace of high-strength fibers to binder hardening of the synthetic resin and placed in to licevyh the grooves of the corresponding cross-section, made in the spacer is placed between the turbine and compressor casing, with one of the annular grooves is open to the compressor, and the other to the turbine, and between the surface of the ring grooves of the spacers and sleeve housed in embossed sleeve with longitudinal corrugations, made of elastic material, while the inner surface of the trunnion-heel covered with a layer of copper and treated with high purity surface, and a thrust magnetic bearing includes a thrust bearing made of a nonmagnetic material, is placed in the cylindrical recess of the corresponding trunnion-heel, between the bottom and surface of the thrust bearing fixed sector of the poles from a material with high magnetic permeability, when this sector of permanent magnets and sector poles made in the form of bars of trapezoidal cross-section in contact with each other by lateral edges, the magnetic sector broad base of its section facing to the bottom of the cylindrical recess, and a narrow base magnetic sectors covered flat wedges of a nonmagnetic material, is rigidly fastened their end surfaces of the end surfaces of the respective poles with the formation of a flat surface which forms with trunnion-fifth of the working gap of the thrust magnetic bearing, in addition, at least radial is the first and the thrust magnetic bearings, posted by turbine, made using a magnetic material with a Curie point of not less than 900°C, while between the thrust bearing and addressed to him by the bottom of the undercut both magnetic bearings, set washer, made in the form composed of washer-like plate of elastic material which is deformed with the formation of annular corrugations, furthermore, the magnetic radial and thrust bearings are fixed against rotation around the longitudinal axis of the shaft, in addition, axial petal gas dynamic bearing includes a spacer and seal of the compressor, the distance between which is placed a ring, while in the cavity between the first and second thrust gas petal bearings, split fifth overall, in the gap between the surface of the cylindrical cavity spacers and addressed to her by the surface of the sleeve placed radial gas dynamic radar bearing.

In addition, corrugated elastic shims placed on the compressor side, filled with an elastic material, bonded with her.

Comparative analysis of the essential features of the proposed solution with the essential features of the prototype and analogues demonstrates its compliance with the criterion of "novelty".

While the essential features of the characterizing part of the claims, solves the trail is the following functional tasks.

Signs indicating that "on the cylindrical sleeve from the side adjacent to the turbine wheel, put the first Cup-shaped pin-heel first thrust magnetic bearing, oriented with its bottom to the turbine wheel, the free end of the shaft has been consistently found to focusing on each other, the second Cup-shaped pin-heel of the second thrust magnetic bearing, oriented with its bottom to the compressor wheel, the first and second thrust petal gas bearings, centrifugal compressor wheel and the balancer washer, fixed nut" form radial and thrust magnetic bearings in addition to gas-dynamic radar that allows the bearings to perceive high dynamic load vibration GTE.

Signs indicating that "each radial magnetic bearing includes a thin-walled sleeve made of nonmagnetic material, on the outer surface of which is uniformly on its circumference are poles, made in the form of bars of trapezoidal cross-section, of a material with high magnetic permeability, between which is placed in contact with the poles of the lateral faces of the magnetic strips of trapezoidal cross-section of magnetic material, on which the entire axial length of magnetized in tangenzialefiera direction" allows the use of electrodynamic forces to maintain the trunnion, i.e. allow in addition to gas-static forces to provide an electrodynamic repulsive forces during the rotation of the axle without sticking segments of permanent magnets to the trunnion. This increases the bearing capacity and stiffness of the radial bearing Assembly.

Signs indicating that magnetic strips broad base of its section facing to the surface of the thin-walled sleeve, and by their narrow grounds placed wedges, designed in the form of strips of non-magnetic material rigidly and flush bonded with the side edges of the poles in contact with the corresponding magnetic strip, forming a cylindrical surface facing in the working gap of the radial magnetic bearing" provide the direction of the main part of the magnetic flux in the area of the working gap of the radial magnetic bearing for receiving considerable electrodynamic forces and ensure the formation of a working clearance with the surface of the trunnion, and provide a smooth cylindrical surface of a magnetic bearing.

Signs indicating that "circular protrusions of the first and second Cup-shaped pins-toe components of the radial magnetic bearings, equipped with a brace of high-strength fibers to binder hardening of the synthetic resin and placed in the annular grooves of the respective poperen the th section, made in the spacer is placed between the turbine and compressor casing" increase the strength of the trunnion, reduce the deformation of the gap magnetic bearings.

Signs indicating that "between the surface of the ring grooves of the spacers and sleeve housed in embossed sleeve with longitudinal corrugations, made of elastic material provide the necessary rigidity of the elastic substrate site in working condition and, accordingly, the damping of forced oscillations of the rotor.

Signs indicating that "the inner surface of the trunnion-heel covered with a layer of copper and treated with high surface cleanliness" provide considerable electrodynamic forces due to the interaction of the eddy currents induced in the pin-heel magnetic field of the magnetic strips and sectors of permanent magnets, with a field of these magnets, which increases the bearing capacity and stiffness of the radial and thrust magnetic bearings.

Signs indicating that "the thrust magnetic bearing includes a thrust bearing made of a nonmagnetic material, is placed in the cylindrical recess of the corresponding trunnion-heel, between the bottom and surface of the thrust bearing fixed sector of the poles from a material with high magnetic permeability, while the sector of permanent magnets and sector poles made in the form of p is independent of trapezoidal cross-section, in contact with each other, the side edges form a thrust magnetic bearing.

Signs indicating that magnetic sector, a broad base of its section facing to the bottom of the cylindrical recess, and a narrow base magnetic sectors covered flat wedges of a nonmagnetic material, is rigidly fastened their end surfaces of the end surfaces of the respective poles with the formation of a flat surface which forms with trunnion-fifth of the working gap of the thrust magnetic bearing to provide direction to the main part of the magnetic flux in the area of the working gap of the thrust magnetic bearing for receiving considerable electrodynamic forces and ensure the formation of a working clearance with the surface of the trunnion, and provide a smooth cylindrical surface of a magnetic bearing.

A sign indicating that "at least radial and thrust magnetic bearings, situated on the side of the turbine, are made using a magnetic material with a Curie point of not less than 900°C prevents demagnetization of the magnetic strips from the action of high temperatures of the turbine and thereby ensures the operability of the magnetic bearing over the entire operating temperature range.

Signs indicating that "between the thrust bearing and the draws to it the bottom of the undercut both magnetic bearings installed spring washer, made in the form composed of washer-like plate of elastic material which is deformed with the formation of annular corrugations provide the necessary rigidity of the elastic substrate of the magnetic bearing is in working condition and prevent jamming of the thrust magnetic bearing operable from uneven thermal expansion of the rotor and spacers.

A sign indicating that the magnetic radial and thrust bearings are fixed against rotation around the longitudinal axis of the shaft prevents rotation of the thrust magnetic bearing under the action of the braking forces.

Signs indicating that "axial petal gas dynamic bearing includes a spacer and seal of the compressor, the distance between which is placed a ring, with a cavity between them, placed first and second thrust petal gas bearings, divided by the total fifth" allow you to absorb the axial load acting on the rotor at the start of the CCD, quenching induced axial oscillations of the rotor.

Signs indicating that "in the gap between the surface of the cylindrical cavity spacers and addressed to her by the surface of the sleeve placed radial gas dynamic radar bearing" help take the radial load acting on the rotor at start-up and shutdown of the CCD to increase stability, the mouth of the RA due to the damping petals.

A sign indicating that "corrugated elastic shims placed on the compressor side, filled with an elastic material, bonded with it" provides the necessary stiffness and damping of the elastic substrate node in working state, and the oscillation of the rotor, due to the axial gas-dynamic forces the turbine and compressor due to the dissipation of the vibration energy of rubber or polyurethane.

Figure 1 shows a longitudinal section of the CCD, as in figure 2, 3 - cross sections of radial-axial magnetic bearing and figure 4 for radar radial gas bearing. Figure 5, 6 shows a local cross section along the axial magnetic bearings.

In the drawings shown, the spacer 1 in the case of the CCD, the shaft 2, the turbine wheel 3, a cylindrical sleeve 4, a centrifugal compressor wheel 5, the first Cup-shaped pin-heel 6, the pin-heel 7 of the second thrust magnetic bearing, the first 8 and second 9 resistant petal gas-dynamic bearings (LGB), balancing washer 10 nut 11, the thin-walled sleeve 12 and 13, the pole 14, 15, 16, 17, magnetic strips 18 and 19, the wedges 20 and 21, working clearances 22 and 23, the annular protrusions 24 and 25 the bands 26 and 27, the annular grooves 28 and 29, ruffled sleeves 30 and 31, a housing 32 and 33 of the magnetic thrust bearings, sector poles 34, 35 and 36, 37 of the thrust magnetic bearing, sector permanent MAGN is tov 38 and 39, flat wedges 40 and 41, the axial clearances 42 and 43, the elastic washer 44 and 45, the pins 46 and 47, the bolts 48 and 49, the distance ring 50, the radial gas dynamic radar bearing 51, a housing 52 axial LGB, the seal 53 cerabino compressor 5, the heel 54 of the thrust LGB, clamps 55 and 56 on thin-walled bushings 12 and 13, the shoulders 57 and 58 of the spacer 1.

The casing of the gas turbine engine includes a spacer 1 disposed between the turbine housings 3 and centrifugal compressor 5. In the cylindrical cavity of the spacer 1 has a rotor with a cylindrical outer surface. The GTE rotor includes a shaft 2, one end of which is rigidly fastened to the impeller of the turbine 3, (for example, by friction welding), on which is mounted a sleeve 4 of the rotor is made with the possibility of gas maintenance, and at the free end fixed centrifugal compressor wheel 5. A cylindrical sleeve 4 is made of a nonmagnetic material such as aluminum alloy AK-1 subjected to the microarc oxidation followed by grinding to obtain high hardness and high surface smoothness. On the cylindrical sleeve 4 adjacent to the turbine wheel 3, placed the Cup-shaped pin-heel 6 radial-thrust magnetic bearing, rigidly fastened to the cylindrical sleeve 4, for example, by welding, oriented with its protrusion 24 to the wheel price is Robinho compressor 5, on the outer surface of which is wearing the brace 26 of a high-strength material, made for example by winding carbon fiber impregnated with a hardening synthetic resins. On the shaft 2 by a centrifugal compressor 5 against the end face of the sleeve 4 mounted pin-heel 7 of the second thrust magnetic bearing, oriented with its lug 25 to the turbine wheel 3, on the outer surface of which is also worn the brace 27 of high-strength material.

Next on the shaft 2 adjacent to the ends of the respective surfaces planted the following details: heel 54 stubborn ORC, a centrifugal compressor wheel 5, the balancing washer 10 and nut 11.

Between the cylindrical sleeve 4 and the inner cavity of the spacer 1 has a radial LGB 51. Symmetrically on both sides of the annular grooves 28 and 29 of the spacer 1 posted by radial magnetic bearings. Symmetrically from two sides in the cylindrical recesses of the spacer 1 is placed thrust magnetic bearings.

Each radial magnetic bearing includes a thin-walled sleeve 12 and 13 made of a nonmagnetic material such as nonmagnetic stainless steel or titanium, on the outer surface of which is uniformly on its circumference are poles 14, 15, 16, 17, made in the form of bars of trapezoidal cross-section, of a material with high magnetic bronzemist the Yu, for example, from an alloy CP, between which is placed the magnetic strips 18 and 19 in contact with the poles 14, 15 and 16, 17 respectively. Magnetic strips 18 and 19 is made, for example, from a material neodymium-iron-boron or samarium-cobalt and throughout the axial length of magnetized in the tangential direction (along the circumference). Magnetic strips 18 and 19 have a trapezoidal cross-sectional shape, wide base facing to the surface of the thin-walled sleeve 12 and 13, and with a narrow base contacts the wedge 20 and 21, made in the form of strips of non-magnetic material rigidly and flush bonded to two adjacent poles 14, 15 and 16, 17. The surface formed by the wedges 20 and 21 and the poles 14, 15, 16, 17 facing the inner surface of the trunnion 6 and 7, is made cylindrical with the formation of the radial gap 22 and 23 with the surface of the trunnion 6 and 7. Between the surface of the spacer 1 and the inner surface of thin-walled bushings 12 and 13 are placed corrugated sleeve 30 and 31 with longitudinal corrugations, made of alloy with prescribed elastic properties, for example HTM. Each radial magnetic bearing fixed against movement along the longitudinal axis in the groove spacers 1 on the one hand by the collar 55 and 56 on the thin-walled sleeve 12 and 13, and on the other side of the collar 57 and 58 of the spacer 1. The inner surface of the trunnion-heel 6 and 7 is covered with a layer of copper and is operated with a high surface finish.

Each thrust magnetic bearing consists of thrust bearing and heel. The thrust bearing includes a housing 32 and 33 in the form of a shallow cylinder, made of non-magnetic material at the bottom of which is fixed (e.g., glue), at least two sectors of permanent magnets 38 and 39 of trapezoidal cross-section (made, for example, from an alloy of neodymium-iron-boron), magnetized in opposite tangential to the adjacent sectors direction (along the circumference), blocked by flat wedges 40 and 41 made of a nonmagnetic material, is rigidly fastened their end surfaces of the end surfaces of the poles 34, 35 and 36, 37 and spaced equally around the circumference between poles 34, 35 and 36, 37 of the alloy with high magnetic permeability, for example CP mounted on the bottom of the casing 32 and 33 of the thrust bearing. Pin-heel 6 and 7 is made Cup-shaped hollow of a nonmagnetic electrically conductive material and forms a thrust bearing axial clearance 42 and 43.

Between the thrust bearing and addressed to him by the bottom of the undercut both magnetic bearings installed elastic washer 44 and 45, made in the form composed of washer-like plate which is deformed with the formation of annular corrugations, of elastic material, such as alloy HTM that prevent jamming of the thrust magnetic bearing operable from uneven thermal expansion R of the torus and spacers 1. Corrugated elastic washer 44 and 45 posted by a centrifugal compressor 5, filled with an elastic material, bonded with her.

To prevent turning of the radial magnetic bearings under the influence of braking forces they are fixed against rotation around the longitudinal axis of the shaft by the pin 46 and 47. To prevent turning of the thrust magnetic bearing under the influence of braking forces around the longitudinal axis of the shaft and axial displacement in the direction of the heel at the start they are fixed by bolts 48 and 49.

Persistent LTP consists of spacers 1, the housing 52 of the thrust orcs, seals 53 a centrifugal compressor 5, the two resistant LGB 8 and 9 located on opposite sides of the abutment 54, and the distance ring 50.

Radial and thrust magnetic bearings, situated on the side of the turbine 3, performed using a magnetic material with a Curie point of not less than 900°C.

Fabricate and assemble radial magnetic bearing as follows. On the outer surface of the thin-walled sleeve 12 have the markings evenly spaced around the circumference of the pole 14, 15, replicas magnetic strips, set between adjacent poles 14, 15 nonmagnetic wedges 20 and weld them to the poles, piercing holes and grind the outer surface on the grinding machine to obtain a desired diameter and surface roughness. Then instead of them is atarov set on the adhesive magnetic strips 18. The resulting sets of poles 14, 15, magnetic strips 18 and nonmagnetic wedges 20 Assembly mounted on the adhesive on the outer surface of the thin-walled sleeve 12. The groove in the housing GTE insert radial magnetic bearings between the sleeve 12 of the magnetic bearing and the spacer 1 is inserted corrugated sleeve 30 is fully inserted in the collar 55 on the sleeve 12 on the one hand and the shoulder 57 on the spacer 1 with the other hand. Similarly produce and collect the second radial magnetic bearing.

The thrust magnetic bearing is collected in the following order. Pre manufactured housing thrust bearing 32 of non-magnetic material, for example aluminum alloy AK-1, in which between the poles 34, 35 evenly spaced around the circumference set simulators sectors of permanent magnets, the latter, in turn, overlapping the nonmagnetic flat wedges 40, weld them together with the formation of a flat surface, polished outer surface. In the notches between the poles 34, 35 pasted sectors of permanent magnets 38 and then paste the resulting sets per body 32 of the thrust bearing. In the spacer 1 set petals radial LGB 51. In the spacer 1 set of annular elastic washer 44 and 45, they establish the collected magnetic thrust bearings and fixed by bolts 48 and 49 from turning and axial displacement in the direction of abutment 54. Similarly with eraut second thrust magnetic bearing.

The pin-heel 6 and 7 are subjected to the microarc oxidation, grind and an internal surface covered with a layer of copper and treated with a high degree of surface cleanliness. The rotor is subjected to dynamic balancing.

Otbalansirovannoy disassemble the rotor for balancing labels. The spacer 1 is inserted, the rotor, with no removable parts. Fix the spacer 1 GTE heat shield consisting of two halves, is placed on the shaft trunnion-heel 7, mounted on the screw body 52 stubborn ORC, then one hard LGB, distance ring 50, the second thrust LGB and fixed with screws seal 53 centrifugal compressor 5. Next, skewer a centrifugal compressor wheel 5, the balancing washer 10 and tighten the nut 11. Other details are collected according to the procedure of assembling the CCD.

Angular contact bearing unit operates as follows. During the rotation of the shell cylindrical sleeve 4 radial LGB and the heel 54 of the thrust LGB appears axial and radial gas dynamic reaction of the gas layer and the rotor floats on the gas lubricating layer. In addition, during the rotation of the trunnion-heel 6 and 7 additionally there electrodynamic forces due to the interaction of eddy currents induced by the magnetic field of the magnetic strips 18 and 19 in the pin-heel 6 and 7 with this field. The radial components of electrodynamically forces acting repulsive way between the trunnion-fifth 6 and 7 and the poles 14, 15 and 16, 17. These forces are summed with the forces of radial LGB acting on the sides of the cylindrical sleeve 4. The corrugations of the corrugated sleeves 30 and 31 and the radial LGB damping forced and self-excited oscillations of the rotor, greatly enhance the stability of the rotor in the form of "half rate of the vortex". The tangential component of the electrodynamic force has a braking effect, but it is not significant. With increasing linear velocity on the surface of the stud-heel 6, 7 repulsive component of the electrodynamic force is increased, and the braking is reduced.

Magnetic and hydrodynamic part of the proposed radial bearing unit automatically implement negative feedback deviation shell cylindrical sleeve 4 and the stud-heel 6, 7 from the coaxial position relative to the point of dynamic equilibrium of the shell of the cylindrical sleeve 4 and the stud-heel 6, 7 in a bearing unit and do not require additional devices (sensors rejection and fast response regulators).

Thrust bearing unit operates as follows. The rotation of the rotor heel 54 POPs up on the gas lubricating layer. During the rotation of the trunnion-heel 6 and 7 additionally there electrodynamic forces due to the interaction of the eddy currents induced in the pin-heel 6 and 7, the magnetic field of segm now permanent magnets 38 and 39 with a field of these magnets. The axial component of the electrodynamic forces acting repulsive way between the trunnion-fifth 6 and 7 and the permanent magnets 38 and 39, and this force is added to the gas forces acting on the heel 54. The tangential component of the electrodynamic force has a braking effect, but it is not significant. With increasing linear velocity on the surface of the stud-heel 6 and 7 of the repulsive component of the electrodynamic force is increased, and the braking is reduced. To increase the electrodynamic thrust bearing Assembly can be applied to the plating surface of the trunnion-heel 6 and 7 facing the sectors of permanent magnets 38 and 39 and the poles 34, 35 and 36, 37, and also to expose her subsequent polishing.

When bilateral, symmetrical design of the axial magnetic bearing unit and gas-dynamical components of the reaction force of the proposed bearing Assembly, acting symmetrically and oppositely directed, automatically implement negative feedback deviation of abutment 54 and the stud-heel 6 and 7 from the equilibrium position and do not require additional devices (sensors rejection and fast response regulators).

1. Gas turbine engine, comprising a housing, a cylindrical cavity which has a rotor with a cylindrical outer surface, comprising a shaft, one to the EC which is rigidly fixed to the impeller of the turbine, on which is mounted the rotor bushing made with the possibility of its gas maintenance, and at the free end of the fixed wheel of a centrifugal compressor provided with a thrust bearing, characterized in that the cylindrical sleeve from the side adjacent to the turbine wheel, put the first Cup-shaped pin-heel first thrust magnetic bearing, oriented with its bottom to the turbine wheel, the free end of the shaft, has been consistently found, with emphasis each other, the second Cup-shaped pin-heel of the second thrust magnetic bearing, oriented with its bottom to the compressor wheel, the first and second thrust petal gas bearings, centrifugal compressor wheel and the balancer washer, fixed nut, with each radial magnetic bearing includes a thin-walled sleeve made of nonmagnetic material, on the outer surface of which is uniformly on its circumference are poles, made in the form of bars of trapezoidal cross-section, of a material with high magnetic permeability, between which is placed in contact with the poles of the lateral faces of the magnetic strips of trapezoidal cross-section of magnetic material, on which the entire axial length of magnetized in opposite tangential direction,the magnetic strips broad base of its section facing to the surface of the thin-walled sleeve, and by their narrow grounds placed wedges, designed in the form of strips of non-magnetic material rigidly and flush bonded with the side edges of the poles in contact with the corresponding magnetic strip, forming a cylindrical surface facing in the working gap of the radial magnetic bearing, in addition, the annular protrusions of the first and second Cup-shaped pins-toe components of the radial magnetic bearings, equipped with a brace of high-strength fibers to binder hardening of the synthetic resin and placed in the annular grooves of the respective cross-section, made in the spacer is placed between the turbine and compressor casing, with one of the annular grooves is open to the compressor, and the other to the turbine, and between the surface of the ring grooves of the spacers and sleeve housed in embossed sleeve with longitudinal corrugations, made of elastic material, while the inner surface of the trunnion-heel covered with a layer of copper and treated with high purity surface, and a thrust magnetic bearing includes a thrust bearing made of a nonmagnetic material, is placed in the cylindrical recess of the corresponding trunnion-heel, between the bottom and surface of the thrust bearing fixed sector of the poles from a material with high magnetic permeability, while the sector p the permanent magnets and sector poles made in the form of bars of trapezoidal cross-section, in contact with each other by lateral edges, the magnetic sector broad base of its section facing to the bottom of the cylindrical recess, and a narrow base magnetic sectors covered flat wedges of a nonmagnetic material, is rigidly fastened their end surfaces of the end surfaces of the respective poles with the formation of a flat surface which forms with trunnion-fifth of the working gap of the thrust magnetic bearing, in addition, at least radial and thrust magnetic bearings, situated on the side of the turbine, are made using a magnetic material with a Curie point of not less than 900°C, while between the thrust bearing and addressed to him bottom undercut both magnetic bearings installed spring washer, made in the form composed of washer-like plate of elastic material which is deformed with the formation of annular corrugations, furthermore, the magnetic radial and thrust bearings are fixed against rotation around the longitudinal axis of the shaft, in addition, axial petal gas dynamic bearing includes a spacer and seal of the compressor, the distance between which is placed a ring, while in the cavity between the first and second thrust petal gas bearings, split fifth overall, in the gap between the surface of the cylinder is practical cavity spacers and addressed to her by the surface of the sleeve placed radial gas dynamic radar bearing.

2. Gas turbine engine according to claim 1, characterized in that the corrugated elastic shims placed on the compressor side, filled with an elastic material, bonded with her.



 

Same patents:

Gas turbine engine // 2528891

FIELD: engines and pumps.

SUBSTANCE: gas turbine engine has cylindrical bush made of nonmagnetic material and fitted on engine shaft. One end of said bush rests against turbine wheel end surface while another end rests against circular ledge of thrust bearing made of nonmagnetic material and fitted on the shaft at section abutting on compressor wheel. Rotor central part comprises aligned shaft and shell ring made of nonmagnetic material jointed together by at least three equally spaced apart equal-depth jumpers made of nonmagnetic material directed radially to rotor lengthwise axis. Rotor and bearing assemblies are fitted inside the spacer of nonmagnetic material with cylindrical case with ends equipped with flanges to be articulated with nozzle diaphragm and compressor diffuser. Note here that shell ring length corresponds to spacer cavity cylindrical part length. Spacer flange side facing the turbine has hole to receive the spinning shaft with bush fitted thereon aligned with spacer lengthwise axis. Besides, this rotor section has the first radial magnetic bearing. For this, said spacer flange is furnished with circular ledge to support composite permanent magnet rigidly secured thereat. Said magnet is composed by at least three permanent magnets. Uneven, extreme magnets are magnetised in rotor axis while even magnets are magnetised radially. Shell ring inner surface has composite permanent magnet including at least three ring permanent magnets. Note here that the quantity, sizes, location and direction of magnetisation of said circular permanent magnets comply with those of permanent magnets secured at spacer flange circular ledge. Housing of second radial magnetic bearing is fitted on cylindrical bush opposite side and on the part of aforesaid circular ledge. For this, it is shaped to disc with hole surrounded by circular ledge facing the rotor centre. Disc surface edges thrust against the surface of ledge composed by first cylindrical recess made at spacer cylindrical end facing the compressor. Disc opposite side has the recess with flat bottom. Note here that composite permanent magnet is rigidly secured o outer surface of said ledge. Said magnet is composed by at least three permanent magnets. Uneven, extreme magnets are magnetised in rotor axis to face by like poles while even magnets are magnetised radially. Composite permanent magnet is rigidly secured at shell ring inner surface facing the compressor. Said magnet is composed by at least three permanent magnets. Note here that the quantity, sizes, location and direction of magnetisation of said circular permanent magnets comply with those of permanent magnets secures at spacer flange circular ledge. Rotor is provided with thrust magnetic bearing including two-side sole and two end thrust bearings. Note here that first end thrust bearings represent disc surface of the second radial magnetic bearing housing provided with ring recess with flat bottom facing the end thrust bearing. Second end thrust bearing made as a disc insert with side facing the end thrust bearing is equipped with circular ledge. Note here that edges of said disc insert thrust against the surface of ledge composed by second cylindrical recess made at the end of first cylindrical recess while its opposite plane faces, with clearance, the compressor wheel. End thrust bearing is composed of a disc locked at rotor shaft and furnished with circular ledges at both sides. Note here that circular recesses with flat bottoms are made at opposite surfaces of the disc. Composite permanent magnets are rigidly fitted at the bottom of the first end thrust bearing second thrust bearing confined by its circular edge. Each of the latter comprises at least three coaxial permanent magnets. Uneven, extreme magnets are magnetised in rotor axis to face by like poles while even magnets are magnetised radially. Besides, composite permanent magnets are rigidly secures at surfaces of circular seats. Each of the latter comprises at least three coaxial permanent magnets. Note here that the quantity, sizes, location and direction of magnetisation of said circular permanent magnets comply with those of permanent magnets secures at spacer flange circular ledge. Magnetic bearing assy arranged on turbine side is made of material with Curie point of at least 900°C.

EFFECT: higher load bearing efficiency and reliability, reliable starting at lower temperatures.

2 dwg

Gas turbine engine // 2528889

FIELD: engines and pumps.

SUBSTANCE: first cup-like journal of the first magnetic bearing assy directed by its bottom to turbine wheel is fitted on engine cylindrical bush adjoining the turbine wheel. Second cup-like journal of the second magnetic bearing assy directed by its bottom to compressor wheel is fitted on rotor section abutting on compressor wheel, on the shaft to thrust there against and against rotor bush end face. Magnetic assemblies of both said cup-like journals comprise structurally identical magnetic elements making the magnetic radial and thrust bearings. For this, bottoms of recesses at said journals are flat while inner and outer inner surfaces of their sidewalls are cylindrical. Composite equal-height permanent magnets are secured at bottoms of aforesaid journals. Each of the latter comprises at least three circular coaxial permanent magnets. Uneven, extreme magnets are magnetised in rotor axis to face by like poles while even magnets are magnetised radially. Three circular permanent magnets of ring identical ID and OD are secured at inner surface of sidewalls at said cup-like journals. Uneven, extreme magnets are magnetised in rotor axis to face by like poles while even magnets are magnetised radially. Circular ledges of the first and second cup-like journals are fitted in circular recesses. The latter are made of nonmagnetic materials and fitted in spacer arranged between housings of turbine and compressor. Surfaces of thee spacer circular grooves facing the bottoms of said journals are flat. Composite permanent magnets are fitted opposite the bottom sections of cup-like journals. Each of the latter comprises at least three coaxial equal-height permanent magnets. Uneven, extreme magnets are magnetised in rotor axis to face by like poles while even magnets are magnetised radially. Note here that the quantity, sizes, location and direction of magnetisation of said circular permanent magnets comply with those of permanent magnets secured at bottoms of cup-like journal recesses. Three circular permanent magnets of ring identical ID and OD are secured at cylindrical surfaces of the spacer circular recesses of appropriate cup-like journals. Uneven, extreme magnets are magnetised in rotor axis to face by like poles while even magnets are magnetised radially. Note here that the quantity, sizes, location and direction of magnetisation of said circular permanent magnets comply with those of permanent magnets secured at inner surface of sidewalls of appropriate cup-like journal. Opposite surfaces of permanent magnets are machined to ensure high-finish flat or cylindrical surfaces with working clearances. Magnetic bearing assy arranged on turbine side is made of material with Curie point of at least 900°C. Note here that cylindrical sections of outer surfaces of said cup-journals are fitted with tread composed of carbon fibre wound thereon and impregnated with synthetic resins.

EFFECT: higher load bearing efficiency and reliability, reliable starting at lower temperatures.

2 dwg

Electric spindle // 2528420

FIELD: electricity.

SUBSTANCE: electric spindle is distinguished for the fact that in the casing cavity there installed are cylindrical bushings coaxially to the stator core cavity, the bushings are made from insulation material, for example, glass fibre plastic, and are coupled by their ends with the ends of the stator core. At least two radial bearings and one thrust magnetic bearing are installed in the end brackets of the electric spindle. Rotor ends are rigidly coupled with the end covers, contacting surfaces of the end shields and cylindrical bushings are fitted by seals. A bearing unit is made so as to be able of magnetic support of the rotor, for this purpose each end cover of the rotor is made from nonmagnetic material and fitted by an annular protrusion turned to the respective end shield made from nonmagnetic material, compound permanent magnets are rigidly fixed one after the other on the inner surface of the annular protrusion. The end shields are equipped by ring-shaped protrusions with at least three annular permanent magnets being rigidly fixed on their outer surface. Additionally, the electric spindle is equipped with an axial magnetic bearing.

EFFECT: increased carrying capacity and stiffness of bearing units, improved efficiency of cooling the winding and core of a stator, improved weight and dimension parameters and increased reliability.

5 cl, 2 dwg

FIELD: electricity.

SUBSTANCE: invention is related to a sensing device to be mounted at the electric machine shaft with a recording unit to record current values of the electric machine bearing. The sensing device to be mounted at the electric machine shaft comprises a recording unit intended to record current values of the electric machine bearing. Further the sensing device comprises an energy converter, which is mounted with the recording unit in a replaceable module, in order to convert mechanical energy of the shaft to electric energy for the recording unit.

EFFECT: designing small-size sensing device with independent power supply.

7 cl, 4 dwg

FIELD: electricity.

SUBSTANCE: control of rotor position is implemented against intensity of external magnet field of magnetic bearings based on permanent magnets which are used as the basic support bearings, data about intensity changes comes to a proportional-integral-differential (PID) controller and power converter, which regulate voltage at two electromagnets controlling the rotor instability. The magnetic bearing control device contains magnetic bearings based on permanent magnets, PID controller, a power converter, two electromagnets, rotor position sensors made as sensors of the external magnet field and installed at the external surface of the device body.

EFFECT: improving accuracy and reliability of the magnetic bearing control.

2 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: shaping method of a rotor deviation signal in magnetic suspension systems of a rotary machine with current control by means of pulse-width modulation (PWM control) in an electromagnet consists in supply of PWM control signals to input of power amplifier 1. From amplifier 1 output the signals in the form of polygonal shaped voltages are supplied to electromagnet 3. At the same time, current signals are supplied to current converter 2 of electromagnet 3 with further extraction of a variable component of sawtooth current. Further, it is converted to a signal proportional to curvature of sawtooth current signal at the switching interval of a PWM control signal, and its further conversion to a rotor deviation signal.

EFFECT: simplifying a self control scheme and creating a simpler sensorless magnetic suspension device, which will allow simplifying the structure of supports of a rotary machine and increasing interference immunity of magnetic suspension systems.

11 cl, 6 dwg

FIELD: machine building.

SUBSTANCE: in compliance with first version, proposed support comprises magnetic system with cyclic alternate magnetic field induced by permanent magnet on one side and, on opposite side, rotor system arranged radially with clearance from magnetic system and made of high-conductivity material. Note here that rotor system is arranged nearby horizontal plane crossing the rotor axle bend curve assy at working rpm. In compliance with second version, magnetic system can radially displace at interaction with rotor system.

EFFECT: better damping characteristics, higher reliability.

24 cl, 9 dwg

FIELD: machine building.

SUBSTANCE: piston machine comprises piston 3 and housing 2. Piston 3 with magnetic bearing slides in housing 2. Device 7 for piston magnetic bearing is fixed relative to housing 2. Linear engine 15 is engaged with piston magnetic bearing.

EFFECT: power conversion without lubrication at lower mechanical costs.

2 cl, 3 dwg

FIELD: machine building.

SUBSTANCE: bearing device and a bearing bracket (1) are proposed from a magnetic radial bearing (4) for contactless support of a shaft (7) of a rotary machine rotor (10) and a supporting bearing (5) for maintenance of the rotor shaft (7). Besides, both bearings (4, 5) are arranged coaxially and strongly connected to each other in the common bearing body (2). Both bearings (4, 5) are elastically suspended relative to the bearing shield (11), the body (12) or the foundation (20) of the rotary machine (10), and the bearing body (2) is elastically suspended relative to the bearing shield (11) or the body (12) of the machine.

EFFECT: development of an improved bearing device and a bearing bracket for a rotary machine, capable of operation in the range of high frequencies of rotation and providing for reduction of impact loads.

12 cl, 5 dwg

FIELD: machine building.

SUBSTANCE: catching bearing (2) has the first supporting body (7) and roller bodies (5), which pass about the imagined geometrical middle axis (M). Each of roller bodies (5) has zone (19) that is located between middle axis (M) and the first supporting body (7). Roller bodies (5) are connected through axis (6) and rolling bearings (11) located on both ends of axis (6) with possibility of being rotated with the first supporting body (7). Bearing (2) has the second supporting body (10) located about the first supporting body (7). Elastic elements (13) are located between supporting body (7) and supporting body (10). Each elastic element (13) has layer (17) from rubber and two layers (18) from metal. Layer (17) from rubber is located between both layers (18) from metal.

EFFECT: creation of a catching bearing, in which there prevented is probability of occurrence of inverse vortex due to minimisation of friction surfaces, and which is applicable for high rotation speeds, as well as for rotary shafts with high weight and requires small place.

25 cl, 3 dwg

Thrust bearing unit // 2529070

FIELD: machine building.

SUBSTANCE: thrust bearing unit consists of a thrust plate and a thrust journal (8). The thrust plate is formed by a casing (1) fitted by a cylindrical groove with flat bottom which is provided by a circular protrusion along the casing (1) perimeter. A resilient gasket (3) is set on the cylindrical groove bottom and a gasostatic bearing rests against it and is made as a ring divided into sectors (5) by oriented metal nonmagnetic patchs (7) coupled with the thrust plate casing. On the side turned to the thrust journal (8) the sector (5) perimeter is fitted by a bead (9) providing for the groove. Gasostatic bearing (6) steps made from antifriction material are fixed in the groove of each sector (5). The patch (7) cross section is of T-shape, the tables of the patchs (7) are made so that radial beads (9) of the sectors (5) can be engaged. External surface of the gasostatic bearing (6) steps is turned to the thrust journal (8) and form an operating clearance with it. In the sectors there provided is a system of communicating channels (12) with the possibility of supplying compressed air to it from an external source, the outlet holes of the system are communicated with the feeding holes (18) in the gasostatic bearing steps, through holes communicating with the operating clearance.

EFFECT: increased carrying capacity of a thrust bearing unit in the operation mode with reduced friction losses in it, decreased deformation of clearance in the thrust bearing unit resulting from the high-pressure of gas blowing, damping of vibrations of a turbomachine rotor caused by axial gas dynamic forces of the turbine or compressor, reliable start-up and shutdown of the turbomachine.

3 cl, 3 dwg

Gas-dynamic bearing // 2496032

FIELD: machine building.

SUBSTANCE: gas-dynamic bearing includes rod, and housing, in which annular carrier card (3) with elastic petals (4) overlapping each other is arranged. Sector slots (5) are made in card (3) opposite petals (4). Carrier card (3) with petals (4) is made of set of plate-like shaped elements (6) attached to each other, for example by spot welding at four points (7). Sizes of plate-like shaped elements (6) are chosen so that solid annular carrier card (3) with petals (4) can be formed at their attachment to each other.

EFFECT: simpler design of gas-dynamic bearing.

5 cl, 4 dwg

FIELD: machine building.

SUBSTANCE: plain thrust bearing from synthetic resin has upper housing (100) from synthetic resin, lower housing (200) from synthetic resin and assembly (300) of thrust bearing from synthetic resin, which is placed between housings (100) and (200). At boundaries of a sliding strip between upper surface of lower annular plate-like section (202) of housing (200), which restricts the lower surface of lower annular groove (204) and lower surface of upper annular plate-like section (102) of housing (100) on one side, and upper surface and lower surface of assembly (300) on the other side, which come into sliding contact with upper and lower surfaces, there is silicon grease based on silicon oil and having kinematic viscosity coefficient at 25°C of not less than 0.0001 m2/s and not more than 0.5 m2/s and containing a thickener to maintain working penetration of not less than 200 and not more than 400. The above silicon oil is silicon oil that contains an additive or modified silicon oil.

EFFECT: creation of plain thrust bearing that is capable of preserving low friction coefficient and preventing microslipping phenomenon at sliding during a long period of time, which allows preventing abnormal friction noise referred to microslipping phenomenon.

12 cl, 9 dwg, 2 tbl

FIELD: transport.

SUBSTANCE: plain thrust bearing (1) made of synthetic resin contains upper body (100) of synthetic resin, lower body (200) of synthetic resin and plain thrust bearing made of synthetic resin assembly (300), fitted between bodies (100) and (200). If to take radial length of body (100) from axis (o) to outer edge surface (303) of the assembly (300), located in lower ring cavity (205) as (r), and thickness of inner edge surface of upper ring plate section (102) as (t), on the upper surface (108) of body (100) there is ring flat surface (109) with circular outer edge, the radius (R) of which, if to take axis (o) of body (100) as centre of circumference, is equal to R=r±t. The thrust bearing (1) is located between lower surface of mounting element at the side of vehicle body and upper surface of spring upper socket, subtending to this lower surface. Due to this, the surface (109) only contacts with lower surface of mounting element at the side of vehicle body.

EFFECT: creation of plain thrust bearing which even under action of variable load such as tilt on mounting element at the side of vehicle body provides smooth operation of steering without interference of upper and lower bodies; higher operation efficiency due to possibility to maintain friction characteristics for a long time.

9 cl, 13 dwg

Turbocompressor // 2469213

FIELD: machine building.

SUBSTANCE: turbocompressor for internal combustion engines includes housing with oil supply, discharge lines, cover plate of housing, shaft with impellers of compressor, turbine, radial and axial sliding bearings and pad plate. Axial sliding bearing is made in the form of two bases, on working surfaces of which oil supply slots and wedge-like grooves are made, which can be adjacent to pad plate. A groove is made on the base on the side of the housing cover plate and forms together with cover plate a cylindrical chamber that is connected to oil supply slots and oil supply line.

EFFECT: improvement of axial sliding bearing operation.

6 dwg

FIELD: machine building.

SUBSTANCE: ring (2') of a support bearing is arranged in the form of a V-belt pulley. At the same time the ring (2') of a thrust bearing shall be arranged mainly in the middle of the total length of a shaft (1) of a turbine expansion engine.

EFFECT: higher load-carrying capacity of a thrust bearing.

2 cl, 4 dwg

Fluid bearing // 2463493

FIELD: machine building.

SUBSTANCE: proposed bearing comprises aligned top and bottom racers 1, 2. Racer 1 is furnished with flute 3 facing said racer to allow maintaining working clearance δ between racers 1, 2. Bearing is provided also with pump 4 to force fluid in working clearance δ. Racer 1 is shaped to annular groove 3 with its walls surrounding, at least section of racer sidewall to allow ring to revolve free. Racer 2 is immersed in working fluid do depth h by gravity G and extra vertical load F in compliance with preset ratio while total cross-section area S1 of side clearances b1 and b2 are calculated by specified formula. Vertical load F at racer 2 does not exceed bearing capacity of the bearing Fmax. Note here that groove sidewalls are vertical as well as mating walls of racer 2.

EFFECT: keeping the large-size circular object twining aroubd the vertical axis.

2 cl, 1 dwg

Machine axis // 2462624

FIELD: machine building.

SUBSTANCE: machine axis represents a rotary body (1) installed at two sides in fixed supports (2). At the ends of the rotary body (1) made from a solid material and fixed supports (2) there are hemispherical grooves (4) to install a ball (5). The diametre of the ball (5) at one end of the rotary body (1) is more than at its other end.

EFFECT: simplified design of a machine axis and reduction of its wear.

3 dwg

FIELD: machine building.

SUBSTANCE: thrust bearing assembly consists of pivot (1), centre pivot (2), in a gap between which a bearing provided with possibility of gas dynamic formation of gas lubrication is arranged, which is equipped with compressed gas supply device to gap (3) between pivot (1) and working surface of bearing. As bearing there used is paddle-type bearing including support (4) and carrying (5) boards made in the form of washers or discs from elastic material, the latter of which forms working surface of bearing. Support board (4) is made in the form of spring structure. Pivot (1) is pressed on shaft (6). Compressed gas supply device is made in the form of through channels (7) made on rear side of pivot (1), the outlet holes (8) of which are distributed along surface of pivot (1), which faces working gap (3), and receiving holes (9) have the possibility of receiving compressed air from external supply at shaft (6) rotation. Shaft (6) is equipped with holes (11) for gas supply inside shaft (6) and has axial hole (12) for gas movement inside shaft (6), as well as holes (13) for gas removal from shaft and its supply to channels (7).

EFFECT: improving reliability and carrying capacity of bearing.

4 dwg

FIELD: mechanics.

SUBSTANCE: invention relates to a plain thrust bearing from synthetic resin, in particular, for thrust bearing suspension rack-type four-wheeled vehicle. The bearing has an upper housing (100), comprising an radial flat spot (102), lower body (200) superimposed on the body (100) with possibility of rotation around the axis of the housing (100) and contains an radial flat spot (202), opposite the site (102 ), and an radial groove (204), performed at the site (202), which is surrounded by the first (203) and second (205) concentric radial projection housing (200). The bearing assembly also includes a node of (300) plain thrust bearing made of disc (304), which is placed in the radial groove (204), is a sliding contact with an radial flat spot (102) and has a circular hole (101), done in the central part . At the same node (300) mounted in an radial groove (204) with an radial gap (AI) between the inner peripheral surface (301) round hole (302) and the outer peripheral surface (207) of the first projection (203) and the radial gap (A2) between the outer peripheral surface (303) disk (304) and an inner peripheral surface (208) of the second projection (205). Node (300) is located in a groove (204) so that its upper surface (305) protrudes from the grooves opening (204) so as to enter into contact slider with the bottom surface (105) housing (100), and its lower surface (306) is in contact slider with the bottom surface (209) groove (204). Housing (100) is combined with the housing (200) by the elastic landing on the housing (200). The sum (A) of the volume of radial gaps (AI) and (A2) is less than the amount (B) of the node part (300), which protrudes from the hole of the groove (204).

EFFECT: time preservation of slipping characteristics such as low coefficient of friction and wear resistance.

7 cl, 12 dwg

FIELD: machine building.

SUBSTANCE: resilient support of a turbomachine rotor comprises a radial bearing set on a shaft with the bearing housing being connected to a stator element, and the stator element is fitted by slits with girders located between them and oriented in the radial direction in respect to the support axis.

EFFECT: invention allows for the reduction of axial dimensions and weight at keeping the required stiffness and reliability.

2 cl, 2 dwg

Up!