CN211343734U - Air bearing, rotor system and micro gas turbine - Google Patents

Abstract

The utility model provides an air bearing, rotor system and miniature gas turbine, include: the bearing body is sleeved on the rotating shaft, a gap is kept between the bearing body and the rotating shaft, the bearing body is an annular cylinder, and a throttling hole is radially arranged on the bearing body; the throttling hole is a variable-diameter hole, and the aperture of an outer wall throttling orifice of the bearing body is larger than that of an inner wall throttling orifice; the bearing comprises a bearing body and is characterized in that an annular groove is formed in the inner wall of the bearing body in the circumferential direction, and the annular groove is partially or integrally intersected with an inner wall throttling orifice. The utility model discloses can be when guaranteeing the solid bearing rigidity, the effectual orifice oxidation of having avoided producing because of high temperature.

Description

Air bearing, rotor system and micro gas turbine

Technical Field

The utility model relates to a bearing technical field especially relates to an air bearing, rotor system and miniature gas turbine.

Background

The bearing clearance of the air bearing is very small, a rotating shaft using the air bearing and an inner ring of the air bearing have high processing precision and assembly precision, the dynamic pressure bearing has higher requirements than a static pressure bearing, the clearance is usually in the order of several microns to tens of microns, and the processing difficulty is very high. In addition, in the normal operation process of the air bearing, when a load acts on the shaft, a wedge-shaped gap is formed between the bearing and the rotating shaft, gas is pressed into the wedge-shaped gap to generate pressure so as to support the load of the bearing, and the minimum gap between the inner ring of the bearing and the rotating shaft is smaller, so that the phenomenon of shaft collision is easily generated, and the bearing is abraded and damaged. In addition, the narrow gap between the stator and the rotor of the air bearing requires that the stator and the rotor must have high machining accuracy and assembling accuracy to prevent collision and abrasion between the stator and the rotor.

The air bearing in the prior art has the following defects:

1. due to the influence of the throttling effect, in order to keep higher bearing rigidity, the aperture of the throttling hole and the air film gap need to be reduced, and the smaller aperture and the smaller gap have great difficulty in processing and manufacturing, so that higher processing and manufacturing cost is brought.

2. In the process of high-speed rotation of the bearing, along with the increase of the rotating speed of the rotor, the temperature in the air film is high, and the throttling hole is easily oxidized in high-temperature air to generate black holes to block the air hole.

The small bearing clearance easily causes abrasion between the rotor and the stator to generate metal chips, so that the throttle hole is blocked, and the reliability of the whole bearing is reduced.

SUMMERY OF THE UTILITY MODEL

In order to solve the technical problem, an object of the present invention is to provide an air bearing rotor system and a micro gas turbine, which can effectively avoid the oxidation of the throttle hole caused by high temperature while ensuring the rigidity of the integral bearing.

The technical scheme of the utility model as follows:

according to an aspect of the present invention, there is provided an air bearing, including: the bearing body is sleeved on the rotating shaft, a gap is kept between the bearing body and the rotating shaft, the bearing body is an annular cylinder, and a throttling hole is radially arranged on the bearing body;

the throttling hole is a variable-diameter hole, and the aperture of an outer wall throttling orifice of the bearing body is larger than that of an inner wall throttling orifice;

the bearing comprises a bearing body and is characterized in that an annular groove is formed in the inner wall of the bearing body in the circumferential direction, and the annular groove is partially or integrally intersected with an inner wall throttling orifice.

Furthermore, the section of the reducing part of the throttling hole is funnel-shaped or conical.

Furthermore, the throttling holes are multiple and are uniformly distributed in a circle or multiple circles along the circumferential direction of the bearing body.

Furthermore, the width W of the annular groove is larger than the diameter D of the throttling hole opening on the inner wall, the throttling hole is positioned in the annular groove,

or the orifice is tangential to one side of the annular groove,

or the orifice hole intersects the annular groove portion.

Furthermore, the width W of the annular groove is equal to the diameter D of the throttling hole on the inner wall, and the throttling hole is tangent to two sides of the annular groove.

Further, the width W of the annular groove < the diameter D of the inner wall throttle orifice, the throttle orifice intersecting with the annular groove portion.

Further, the depth H of the annular groove is more than or equal to the diameter D of the throttling orifice of the inner wall.

Further, the width of a bearing gap between the bearing body and the rotating shaft is w, and the diameter of the inner wall throttling orifice is D;

wherein D < w < 3D.

According to another aspect of the present invention, there is provided a rotor system, comprising the above-mentioned air bearing.

According to another aspect of the present invention, there is provided a micro gas turbine, comprising the rotor system described above.

Compared with the prior art, the utility model discloses following beneficial effect has:

in the utility model, because the throttle hole part or the whole throttle hole part sinks into the annular groove, when the shaft and the inner wall of the radial bearing generate friction, the throttle hole in the annular groove can not be abraded, the throttle hole is prevented from being blocked, thereby improving the pneumatic lubrication effect; the annular groove can increase the position clearance of the throttling hole, and the throttling hole oxidation caused by high temperature is effectively avoided while the rigidity of the whole bearing is ensured.

Drawings

Fig. 1 is a front view of the air bearing structure of the present invention.

Fig. 2 is a cross-sectional view taken along line a-a of fig. 1.

Fig. 3 is a partial enlarged view of a bearing orifice according to the present invention.

Fig. 4 is a first structural view of the anti-rotation component of the radial bearing of the present invention.

Fig. 5 is a cross-sectional view taken along line a-a of fig. 4.

Fig. 6 is a structural diagram of a rotation-preventing member of the radial bearing of the present invention.

Fig. 7 is a cross-sectional view taken along line a-a of fig. 6.

Fig. 8 is a third structural view of the anti-rotation component of the radial bearing of the present invention.

Fig. 9 is a cross-sectional view taken along line a-a of fig. 8.

Fig. 10 is a fourth structural view of the anti-rotation component of the radial bearing of the present invention.

Fig. 11 is a cross-sectional view taken along line a-a of fig. 10.

Fig. 12 is a fifth structural view of the anti-rotation component of the radial bearing of the present invention.

Fig. 13 is a cross-sectional view taken along line a-a of fig. 12.

Fig. 14 is a sixth structural view of an anti-rotation member of the radial bearing of the present invention.

Fig. 15 is a cross-sectional view taken along line a-a of fig. 14.

Fig. 16 is a first structural view of the rotor system of the present invention.

Fig. 17 is a second structure diagram of the rotor system of the present invention.

Fig. 18 is a schematic view of the thrust bearing assembly of the present invention.

Fig. 19 is a schematic structural view of the first air tank of the present invention.

Fig. 20 is a schematic view of the radial bearing assembly of the present invention.

Fig. 21 is a schematic structural view of a second air tank according to the present invention.

Fig. 22 is a structure diagram of the multi-type second air tank assembly of the present invention.

Fig. 23 is a first structural view of an anti-rotation member of the thrust bearing of the present invention.

Fig. 24 is a cross-sectional view taken along line a-a of fig. 23.

Fig. 25 is a second structural view of an anti-rotation member of the thrust bearing of the present invention.

Fig. 26 is a cross-sectional view taken along line a-a of fig. 25.

Fig. 27 is a third structural view of an anti-rotation member of the thrust bearing of the present invention.

Fig. 28 is a cross-sectional view taken along line a-a of fig. 27.

Fig. 29 is a fourth structural view of an anti-rotation member of the thrust bearing of the present invention.

Fig. 30 is a cross-sectional view taken along line a-a of fig. 29.

Fig. 31 is a fifth structural view of an anti-rotation member of the thrust bearing of the present invention.

Fig. 32 is a cross-sectional view taken along line a-a of fig. 31.

Fig. 33 is a sixth structural view of an anti-rotation member of the thrust bearing of the present invention.

Fig. 34 is a sectional view taken along a-a in fig. 33.

Detailed Description

In order to better understand the technical solution of the present invention, the present invention will be further explained with reference to the following specific embodiments and the accompanying drawings.

According to an aspect of the present invention, an air bearing is provided.

As shown in fig. 1, 2 and 3, the air bearing includes a second bearing housing 230 and a bearing body 220 which are sequentially nested from outside to inside, a rotating shaft 110 is arranged in the bearing body 220, the bearing body 220 is an annular cylinder, a throttle hole 270 is radially arranged on the bearing body 220, the throttle hole 270 is a diameter-variable hole, an outer wall throttle hole 270 of the bearing body 220 is larger than an inner wall throttle hole 270, an annular groove 260 is circumferentially arranged on the inner wall of the bearing body 220, and the inner wall throttle hole 270 intersects with the annular groove 260 partially or integrally.

Preferably, the air bearing may be one of a hydrostatic bearing, a hydrodynamic bearing, or a hybrid bearing of dynamic and static pressure.

Preferably, the cross section of the diameter-variable portion of the orifice 270 is funnel-shaped or conical.

Preferably, the throttle holes 270 are plural and are uniformly distributed in one or more circles along the circumferential direction of the bearing body 220.

Preferably, the orifice 270 is positioned at an axial load so that the air film pressure in the bearing gap in the axial direction is uniformly distributed.

Preferably, the width W of the annular groove 260 is larger than the diameter D of the inner wall throttle opening, and the throttle hole 270 is located in the annular groove 260, or the throttle hole 270 is tangent to one side of the annular groove 260, or the throttle hole 270 partially intersects the annular groove 260.

Preferably, the width W of the annular groove 260 is equal to the inner wall throttling orifice diameter D, and the throttling orifice 6 is tangent to both sides of the annular groove 4.

Preferably, the annular groove 260 has a width W < the inner wall orifice diameter D, and the orifice hole 270 partially intersects the annular groove 260.

Preferably, the depth H of the annular groove 260 is more than or equal to the diameter D of the throttling orifice of the inner wall.

Preferably, a width of a bearing gap between the bearing body 220 and the rotating shaft 110 is w, D < w <3D, and preferably, w is 1.5D.

In the air bearing structure provided by the utility model, because the throttling hole 270 is partially or completely sunk into the annular groove 260, when the shaft and the inner wall of the radial bearing generate friction, the throttling hole 270 in the annular groove can not be worn, the throttling hole is prevented from being blocked, and the pneumatic lubrication effect is improved; the annular groove 260 can increase the position clearance of the throttling hole 270, and the throttling hole oxidation caused by high temperature is effectively avoided while the rigidity of the whole bearing is ensured.

In the embodiment of the present invention, an anti-rotation structure for the radial bearing is further provided.

The anti-rotation radial bearing 200 of the present embodiment is used to be mounted to the rotating shaft 110 to support the rotating shaft 110 in the radial direction. The radial bearing 200 includes a bearing body 220, a second bearing housing 230, a second bearing end cap 240, and a second anti-rotation member 250, wherein the bearing body 220 is sleeved on the rotating shaft 110 and keeps a predetermined gap with the rotating shaft 110, the second bearing housing 230 is covered on an axial end surface and an outer periphery of the bearing body 220, and the second bearing end cap 240 is sleeved on the rotating shaft 110 and abuts against an end surface of the second bearing housing 230; the second rotation preventing member 250 is disposed between the second bearing housing 230 and the bearing body 220 and connects them to fix the bearing body 220 in the circumferential direction.

In this embodiment, one end of the second anti-rotation member 250 is fixedly connected to or integrally formed with the second bearing housing 230, and the other end of the second anti-rotation member 250 is detachably connected to the bearing body 220;

alternatively, one end of the second rotation-preventing member 250 is detachably connected to the second bearing housing 230, and the other end of the second rotation-preventing member 250 is fixedly connected to the bearing body 220 or integrally formed therewith. This manner of attachment of the second anti-rotation member 250 can make installation of the second anti-rotation member 250 very convenient.

Specifically, the second anti-rotation member 250 may be provided in one or more.

The present embodiment provides the following specific structure for the second anti-rotation member 250.

As shown in fig. 4 and 5, in the present embodiment, the second rotation-preventing member 250 is provided as a pin and is fixedly mounted on the end surface of the bearing body 220, and the second bearing housing 230 is provided with a corresponding fourth receiving hole 231, so that the circumferential positioning of the bearing body 220 is realized by the pin.

As shown in fig. 6 and 7, in the present embodiment, the second rotation-preventing member 250 is provided as a pin and is fixedly mounted on the end surface of the second bearing housing 230 facing the bearing body 220, and the bearing body 220 is provided with a corresponding fifth receiving hole 221, so that the circumferential positioning of the bearing body 220 is realized by the pin.

As shown in fig. 8 and 9, in the present embodiment, the second rotation-preventing member 250 is provided as a pin or a dowel, the second rotation-preventing member 250 is installed from the outer periphery of the second bearing housing 230 in the radial direction of the second bearing housing 230, one end of the second rotation-preventing member 250 is fixed to the second bearing housing 230, the other end is inserted into the outer periphery of the bearing body 220, the outer periphery of the bearing body 220 is provided with a corresponding sixth receiving hole 222, and circumferential positioning of the bearing body 220 is achieved by the pin or the dowel.

As shown in fig. 10 and 11, in the present embodiment, the second rotation-preventing member 250 is provided as a key and is fixedly mounted on the end surface of the bearing body 220 or integrally formed with one end surface of the bearing body 220, and the second bearing housing 230 is provided with a corresponding third key groove 232, so that the circumferential positioning of the bearing body 220 is realized by the key.

As shown in fig. 12 and 3, in the present embodiment, the second rotation-preventing member 250 is provided as a key and is fixedly mounted on the inner diameter surface of the second bearing housing 230, or is integrally formed with the inner diameter surface of the second bearing housing 230, and the bearing body 220 is provided with a corresponding fourth key groove 223, so that the circumferential positioning of the bearing body 220 is realized by the key.

As shown in fig. 14 and 15, in the present embodiment, the second rotation-preventing member 250 is provided as a spherical body and is fixedly mounted on the end surface of the bearing body 220, and the second bearing housing 230 is provided with a corresponding hemispherical groove, so that the circumferential positioning of the bearing body 220 is achieved by the spherical body.

As shown in fig. 14 and 15, in the present embodiment, the second rotation-preventing member 250 may be provided with a spherical body and fixedly mounted on the end surface of the second bearing housing 230 facing the bearing body 220, and the bearing body 220 is provided with a corresponding semi-spherical groove, and the circumferential positioning of the bearing body 220 is realized by the spherical body.

In the present invention, the specific form of the anti-rotation members of the above embodiments is only an exemplary illustration of the preferred structure of the anti-rotation members, and does not constitute a limitation of the present invention, it should be understood that any member that is disposed between the bearing housing and the bearing body can prevent the bearing body from rotating along the circumferential direction belongs to the protection scope of the present invention.

The utility model discloses a radial air bearing is suitable for high-speed and hypervelocity rotatory rotor system, perhaps the great rotor system of shaft diameter, and at the operation in-process of rotor, bearing body job stabilization can not take place to rotate along with the improvement of the 110 rotational speeds of pivot, the dependable performance, long service life, and simple structure.

The embodiment of the utility model provides an use the rotor system of above-mentioned bearing still.

As shown in fig. 16, the rotor system includes a rotating shaft 110, a shaft body of the rotating shaft 110 is an integral structure, the rotating shaft 110 is horizontally or vertically disposed, and a thrust bearing 100, a first radial bearing 200, a motor 300, a second radial bearing 400, a compressor 500, and a turbine 600 are sequentially sleeved on the rotating shaft 110.

As shown in fig. 17, the rotor system includes a rotating shaft 110, a shaft body of the rotating shaft 110 is an integral structure, the rotating shaft 110 is horizontally or vertically disposed, and a first radial bearing 200, a motor 300, a second radial bearing 400, a compressor 500, a thrust bearing 100, and a turbine 600 are sequentially sleeved on the rotating shaft 110.

For the rotor system shown in fig. 16, the side surface of the rotating shaft 110 is easily worn, air is easily accumulated at the worn position after the wear, the temperature is increased to 800-.

For the rotor system shown in fig. 17, there are 4 right angle bends in the shaft system and the air flow path resistance is severe.

In order to solve the problems of the rotor system, the present invention provides a first air groove 800 in the thrust bearing 100, and a second air groove 900 in the rotating shaft 110 and/or the radial bearing to improve the air circulation rate; meanwhile, the air groove oblique angle is arranged at the position of the thrust bearing 100, so that active flow guide of gas can be realized.

In the present embodiment, a structure of a thrust bearing 100 is provided, as shown in fig. 18, the thrust bearing 100 includes a second thrust disk 121, a second stator 140, a first stator 130, and a first thrust disk 122, the second stator 140 and the first stator 130 form a bearing stator 180, and the second thrust disk 121 and the first thrust disk 122 form a thrust disk 120. The second thrust disc 121, the second stator 140, the first stator 130, and the first thrust disc 122 are sequentially sleeved on the rotating shaft 110, the end surface of the second stator 140 facing the second thrust disc 121 side or the end surface of the second thrust disc 121 facing the second stator 140 side is provided with a first air groove 800, the end surface of the first stator 130 facing the first thrust disc 122 side or the end surface of the first thrust disc 122 facing the first stator 130 side is provided with a first air groove 800, a gap is formed between the second stator 140 and the second thrust disc 121, a gap is formed between the first stator 130 and the first thrust disc 122, and the second thrust disc 121, the first thrust disc 122, and the rotating shaft 110 are fixedly connected. A sealing ring may be disposed on an end surface of the second stator 140 adjacent to the first stator 130, and an elastic member 190 may be disposed between the second stator 140, the first stator 130, and the bearing housing. In the above thrust bearing 100 structure of the present invention, as shown in fig. 19, the first air groove 800 is an arc-shaped groove, the arc-shaped groove is circumferentially and evenly distributed and centrally symmetrical, one end of the arc-shaped groove is adjacent to the center of the circle, and the other end is adjacent to the circumference or intersects with the circumference.

The number of the arc-shaped grooves is set according to the rotating speed of the rotating shaft 110, so that the air flow rate and the pressure reach reasonable proportion, the rigidity and the load capacity of the bearing can be kept to be high under the condition that the rotating shaft 100 rotates in the forward direction or in the reverse direction, the air through flow is smooth, and the air can be prevented from being blocked in the flow channel.

In the arc-shaped groove structure of the thrust bearing 100, when the rotating shaft 110 rotates clockwise as seen from the air inlet direction, the arc-shaped grooves on the end surfaces of the second thrust disc 121 and the first thrust disc 122 are left concave arcs, the arc-shaped grooves on the end surfaces of the second stator 140 and the first stator 130 are right concave arcs, when the rotating shaft 110 rotates counterclockwise, the arc-shaped grooves on the end surfaces of the second thrust disc 121 and the first thrust disc 122 are right concave arcs, and the arc-shaped grooves on the end surfaces of the second stator 140 and the first stator 130 are left concave arcs, so that the air flows through from left to right along the axial direction. Namely, the suction type first air groove 800 is arranged on the left side of the thrust bearing 100, and the throw type first air groove 800 is arranged on the right side of the thrust bearing, so that the rapid through flow of air in the bearing can be realized, the gas of the compressor can be conducted, and the air blockage and accumulation can be prevented.

Preferably, the first air groove 800 may be formed by forging, rolling, etching, or punching.

Preferably, the second thrust disk 121 and the first thrust disk 122 are made of a stainless steel material, which facilitates the machining of the first air groove 800.

In the present embodiment, a radial bearing structure is provided, which is suitable for the first radial bearing 200 and the second radial bearing 400.

As shown in fig. 20, the radial bearing includes a bearing body 220, and a second air groove 900 is provided on a circumferential surface of the rotating shaft 110 corresponding to a position where the bearing body 220 is mounted or on an inner wall of the bearing body 220 in a circumferential direction. When the rotating shaft 110 rotates and gradually accelerates, the flowing gas existing in the bearing gap is pressed into the second air groove 900 and rapidly flows through the second air groove 900, so that the directional high-speed circulation of the gas is realized, and under the condition of meeting the bearing air pressure load, the rotating shaft 110 and the radial bearing can better dissipate heat and guide flow.

Preferably, the second air groove 900 may be formed by forging, rolling, etching, or punching.

Preferably, as shown in fig. 21, the secondary air slot 900 is in the shape of a parallel diagonal slot or a spiral slot having a smaller flow capacity than the parallel diagonal slot but increased axial damping than the parallel diagonal slot. The circulation of air in-process, when the pitch is less, the air flow can the pressure boost that slows down, and when the pitch is great, the air flow can the acceleration rate step-down, therefore can set up the helicla flute parameter according to the rotation axis rotational speed, when the rotation axis rotational speed is high, sets up the helicla flute and be coarse pitch, and the helix clearance is loose, and when the rotation axis rotational speed was low, it is little pitch to set up the helicla flute, and the helix clearance is fine and close.

Preferably, the parallel chutes are continuous or discontinuous.

Preferably, the helical groove has a lead angle α, a pitch P, a depth HL, a diameter DL of the rotation axis, 30 ° < α <60 °, 1/2DL < P <5DL,

preferably, P is 3DL and α is 45 °.

Preferably, the helical groove makes half a turn or 1/3 turns around the shaft.

Preferably, the parallel inclined grooves or the spiral grooves are positioned such that the rigidity and the load capacity of the bearing are maintained when the rotating shaft 110 rotates in the forward direction or in the reverse direction, and air flows smoothly, thereby preventing air from being blocked in the flow passage.

Preferably, the second air groove 900 of the bearing body 220 is provided at a middle portion of the rotation shaft 100 corresponding to a position where the inner wall of the bearing body 220 is installed, or provided at two independent portions symmetrically distributed at both sides of the middle portion.

Preferably, the air inlet end of the parallel inclined groove or the spiral groove on the rotating shaft 110 is adjacent to the annular groove.

Preferably, when the rotating shaft 110 rotates clockwise as viewed from the air intake direction, the inclined direction of the parallel diagonal grooves or the helical grooves is inclined to the left, and when the rotating shaft 110 rotates counterclockwise, the inclined direction of the parallel diagonal grooves or the helical grooves is inclined to the right, so that air flows through the rotating shaft from the left to the right in the axial direction.

Preferably, as shown in fig. 22, the shape of the second air groove 900 further includes a chevron shape, a figure eight shape, a V shape, a chevron shape groove, or a V shape groove, and the bearing is configured to support the rotating shaft 110 in a desired manner in a non-contact manner under the condition that the rotating shaft 110 rotates in a forward direction or a reverse direction, and has high load capacity and good stability.

Splayed grooves, herringbone grooves or V-shaped grooves are arranged at the positions of the rotating shaft 110 with larger load or insufficient rigidity, parallel inclined grooves or spiral grooves are arranged at the positions with insufficient through-flow, and the splayed grooves, the herringbone grooves, the V-shaped grooves and/or the parallel inclined grooves and the spiral grooves are arranged at intervals.

Preferably, the first radial bearing 200, the second radial bearing 400, and the thrust bearing 100 are one of a hydrostatic bearing, a hydrodynamic bearing, and a hybrid dynamic-static bearing.

In the present invention, the ventilation efficiency of the second air groove 900 varies according to the angle, the groove width, the number of grooves, the length, the depth, and the flatness of the second air groove 900, and the ventilation speed is related to the rotation speed of the rotating shaft 110 and the bearing gap. In addition, in reality, the cross section of the rotating shaft 110 cannot be an ideal circle, when the out-of-roundness affects the pressure of the air film during rotation, the radial distribution of the gap between the rotating shaft 110 and the bearing body 220 is not uniform, the pressure of the space with a small gap becomes large, and the pressure of the place with a large gap becomes small. The second air groove 900 and the annular groove may be arranged in a matching manner according to actual conditions.

Preferably, the same direction air grooves are engraved on the thrust disc 120, the rotating shaft 110 or the bearing body 220, wherein the air grooves are engraved on the rotating shaft or the shaft sleeve surface equivalently.

Preferably, the air groove is engraved on the rotating shaft 110, and since the rotating shaft 110 is hard and wear-resistant, the air groove is not easily deformed and worn when receiving impact, wherein the air groove is engraved at one end, both ends, or a specific position of the rotating shaft.

The embodiment of the utility model provides a thrust bearing 100 to rotor system still provides a thrust bearing's anti-rotation structure for stability when guaranteeing the bearing use.

The anti-rotation thrust bearing 100 of the present embodiment is adapted to be mounted to the rotating shaft 110 to support the rotating shaft 110 in the axial direction. The anti-rotation thrust air bearing 100 comprises a thrust disc 120, a first stator 130, a second stator 140, a first bearing shell 150, a first bearing end cover 160 and a first anti-rotation component 170, wherein the thrust disc 120 is fixedly installed on the rotating shaft 110 or integrally formed with the rotating shaft 110, the first stator 130 is sleeved on the rotating shaft 110 and is positioned on one side of the thrust disc 120, a preset gap is reserved between the first stator 130 and the thrust disc 120, the second stator 140 is sleeved on the rotating shaft 110 and is positioned on the other side of the thrust disc 120, a preset gap is reserved between the second stator 140 and the thrust disc 120, and the first bearing shell 150 is sleeved on the peripheries of the first stator 130 and the second stator 140 and the end face of the first stator 130; the first bearing end cap 160 is sleeved on the rotating shaft 110, is positioned on one side of the second stator 140, and is abutted against the end surface of the second stator 140, and the first stator 130 and the second stator 140 are fixedly connected to form a bearing stator 180; the first rotation preventing member 170 is disposed between the first bearing housing 150 and the bearing stator 180 and connects the two to fix the bearing stator 180 in the circumferential direction.

In an embodiment, one end of the first anti-rotation member 170 is fixedly connected or integrally formed with the first bearing housing 150, and the other end of the first anti-rotation member 170 is detachably connected with the bearing stator 180;

alternatively, one end of the first rotation-preventing member 170 is detachably connected to the first bearing housing 150, and the other end of the first rotation-preventing member 170 is fixedly connected to the bearing stator 180 or integrally formed therewith. This connection of the first anti-rotation member 170 enables the first anti-rotation member 170 to be mounted very conveniently.

Specifically, the first anti-rotation member 170 may be provided in one or more.

The connection between the first anti-rotation member 170 and the bearing stator 180 may be with the first stator 130 or with the second stator 140, and because the first stator 130 and the second stator 140 are fixedly connected, the first anti-rotation member 170 can prevent the bearing stator 180 from rotating circumferentially regardless of which stator is connected.

The present embodiment provides the following specific structure for the first anti-rotation member 170.

As shown in fig. 23 and 24, in the present embodiment, the first rotation-preventing member 170 is provided as a pin and is fixedly mounted on the end surface of the bearing stator 180, and the first bearing housing 150 is provided with a corresponding first receiving hole 151, and circumferential positioning of the bearing stator 180 is achieved by the pin.

As shown in fig. 25 and 26, in the present embodiment, the first rotation-preventing member 170 is provided as a pin and is fixedly mounted on the end surface of the first bearing housing 150 facing the bearing stator 180, and the bearing stator 180 is provided with a corresponding second receiving hole 181, and circumferential positioning of the bearing stator 180 is achieved by the pin.

As shown in fig. 27 and 28, in the present embodiment, the first rotation preventing member 170 is provided as a pin or a dowel, the first rotation preventing member 170 is installed from the outer periphery of the first bearing housing 150 in the radial direction of the first bearing housing 150, one end of the first rotation preventing member 170 is fixed to the first bearing housing 150, the other end is inserted into the outer periphery of the bearing stator 180, the outer periphery of the bearing stator 180 is provided with a corresponding third receiving hole 182, and circumferential positioning of the bearing stator 180 is achieved by the pin or the dowel.

As shown in fig. 29 and 30, in the present embodiment, the first rotation-preventing member 170 is provided as a key and is fixedly mounted on an end surface of the bearing stator 180 or is integrally formed with one end surface of the bearing stator 180, and the first bearing housing 150 is provided with a corresponding first key groove 152, so that the circumferential positioning of the bearing stator 180 is realized by the key.

As shown in fig. 31 and 32, in the present embodiment, the first rotation-preventing member 170 is provided as a key and is fixedly mounted on the inner diameter surface of the first bearing housing 150, or is integrally formed with the inner diameter surface of the first bearing housing 150, and the bearing stator 180 is provided with a corresponding second key groove 183, so that the circumferential positioning of the bearing stator 180 is realized by the key.

As shown in fig. 33 and 34, in the present embodiment, the first rotation-preventing member 170 is provided as a spherical body and is fixedly mounted on the end surface of the bearing stator 180, and the first bearing housing 150 is provided with a corresponding first hemispherical groove, by which circumferential positioning of the bearing stator 180 is achieved.

As shown in fig. 33 and 34, in the present embodiment, the first rotation-preventing member 170 is provided as a spherical body and is fixedly mounted on the end surface of the first bearing housing 150 facing the bearing stator 180, and the bearing stator 180 is provided with a corresponding semi-spherical groove, and circumferential positioning of the bearing stator 180 is achieved by the spherical body.

In the present invention, the specific forms of the anti-rotation members of the above embodiments are merely illustrative of the preferred structures of the anti-rotation members, and do not limit the present invention. Meanwhile, the above structures are directed to the structure in which the thrust disk 120 is located between the bearing stators 180, and the above anti-rotation member is also applicable to the structure in which the bearing stators 180 are located between the thrust disks 120. It should be understood that any component that is disposed between the bearing housing and the bearing stator and that can prevent the bearing stator from rotating in the circumferential direction belongs to the protection scope of the present invention.

The micro gas turbine applied to the air bearing is a newly developed small heat engine, the single-machine power range of the micro gas turbine is 25-300 kW, and the basic technical characteristics are that a radial-flow impeller machine and a regenerative cycle are adopted. The micro gas turbine has a simple and compact structure, saves the installation space, is convenient for quick installation and transportation, and can well meet the small-scale and distributed requirements of distributed power supply; the moving parts are few, the structure is simple and compact, and therefore the reliability is good, and the manufacturing cost and the maintenance cost are low; good environmental adaptability and high power supply quality.

The whole system only has one moving part and adopts an air bearing, the operation reliability of the system is as high as 99.996%, and the average annual downtime and overhaul time is not more than 2 hours. The utility model discloses a bearing/rotor system can be used to the miniature gas turbine of 10 ~ 100KW models, like the 15/30/45KW model. The utility model discloses a miniature gas turbine can be with step power, step rotational speed operation, and the highest rotational speed reaches 140000RPM, and the fuel quantity is few.

The above description is only a preferred embodiment of the application and is illustrative of the principles of the technology employed. It will be understood by those skilled in the art that the scope of the present invention is not limited to the specific combination of the above-mentioned features, but also covers other embodiments formed by any combination of the above-mentioned features or their equivalents without departing from the spirit of the present invention. For example, the features described above have similar functions to (but are not limited to) those disclosed in this application.

Claims (10)

1. An air bearing, comprising: the bearing body is sleeved on the rotating shaft, a gap is kept between the bearing body and the rotating shaft, the bearing body is an annular cylinder, and a throttling hole is radially arranged on the bearing body;

the throttling hole is a variable-diameter hole, and the aperture of an outer wall throttling orifice of the bearing body is larger than that of an inner wall throttling orifice;

the bearing comprises a bearing body and is characterized in that an annular groove is formed in the inner wall of the bearing body in the circumferential direction, and the annular groove is partially or integrally intersected with an inner wall throttling orifice.

2. The air bearing of claim 1, wherein the orifice reducing portion is funnel-shaped or cone-shaped in cross section.

3. The air bearing of claim 1, wherein the orifice is a plurality of orifices, and the orifices are evenly distributed in one or more circles along the circumferential direction of the bearing body.

4. An air bearing according to claim 1 wherein the annular groove width W > inner wall restriction orifice diameter D, the restriction orifice being located within the annular groove,

or the orifice is tangential to one side of the annular groove,

or the orifice hole intersects the annular groove portion.

5. An air bearing according to claim 1 wherein the annular groove has a width W equal to the inner wall orifice diameter D, the orifice being tangential to both sides of the annular groove.

6. An air bearing according to claim 1 wherein the annular groove width W < inner wall restriction orifice diameter D, the restriction orifice intersecting the annular groove portion.

7. An air bearing according to claim 1 wherein the annular groove depth H ≧ the inner wall throttle orifice diameter D.

8. The air bearing of claim 1, wherein a bearing gap width between the bearing body and the rotating shaft is w, and the inner wall orifice diameter is D;

wherein D < w < 3D.

9. A rotor system comprising an air bearing according to any of claims 1 to 8.

10. A micro gas turbine comprising the rotor system of claim 9.

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