CN211343735U - Radial air bearing, rotor system and micro gas turbine - Google Patents

Abstract

The utility model provides a radial air bearing for install the pivot, in order to upwards support the pivot, include: the bearing comprises a bearing body, a second bearing shell, a second bearing end cover and a second anti-rotation component; the bearing body is sleeved on the rotating shaft, a preset gap is kept between the bearing body and the rotating shaft, the second bearing shell is covered on one axial end face and the periphery of the bearing body, and the second bearing end cover is sleeved on the rotating shaft and abutted against one end face of the second bearing shell; the second rotation-preventing member is disposed between the second bearing housing and the bearing body and connects the second rotation-preventing member and the bearing body to fix the bearing body in the circumferential direction. The utility model discloses can make the bearing steady operation at the high-speed operation in-process of rotor, can not take place to rotate along with the improvement of rotor rotational speed.

Description

Radial air bearing, rotor system and micro gas turbine

Technical Field

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

Background

The radial air bearing realizes the supporting function by means of compressed air between a shaft and a bearing inner ring, and because mechanical friction does not exist in the working process, the fixing problem of the radial air bearing is rarely considered in the general design process. In the prior art, for a radial air bearing, a rubber ring is usually installed between the outer diameter of the bearing and a bearing seat, and the bearing is fixed by means of friction force between the rubber ring and the outer diameter of the bearing to prevent circumferential rotation of the bearing. However, in the practical application of the radial air bearing, when the rotating speed of the rotating shaft reaches more than about 10 thousands of revolutions, the friction between the compressed air film and the rotating shaft is increased, and the torque generated by the friction force makes the radial air bearing rotate along with the rotating shaft more obviously and frequently. And along with the further improvement of the rotating speed of the rotating shaft or the increase of the shaft diameter of the rotating shaft, the friction force between the air film and the inner diameter of the radial air bearing is further increased, the rotating speed of the radial air bearing relative to the bearing seat is increased, and the rubber ring is easy to wear and damage.

SUMMERY OF THE UTILITY MODEL

In order to solve the technical problem, an object of the utility model is to provide a radial air bearing, rotor system and miniature gas turbine can make the bearing steady operation at the high-speed operation in-process of rotor, can not take place to rotate along with the improvement of rotor rotational speed.

The technical scheme of the utility model as follows:

according to an aspect of the present invention, there is provided a radial air bearing for mounting to a rotating shaft to radially support the rotating shaft, comprising:

the bearing comprises a bearing body, a second bearing shell, a second bearing end cover and a second anti-rotation component;

the bearing body is sleeved on the rotating shaft, a preset gap is kept between the bearing body and the rotating shaft, the second bearing shell is covered on one axial end face and the periphery of the bearing body, and the second bearing end cover is sleeved on the rotating shaft and abutted against one end face of the second bearing shell;

the second rotation-preventing member is disposed between the second bearing housing and the bearing body and connects the second rotation-preventing member and the bearing body to fix the bearing body in the circumferential direction.

Furthermore, one end of the second anti-rotation component is fixedly connected with the second bearing shell or integrally formed, and the other end of the second anti-rotation component is detachably connected with the bearing body;

or one end of the second anti-rotation component is detachably connected with the second bearing shell, and the other end of the second anti-rotation component is fixedly connected with the bearing body or integrally formed.

Furthermore, the second rotation-preventing component is provided with a pin and is fixedly arranged on the end surface of the bearing body, and a corresponding fourth accommodating hole is formed in the second bearing shell;

or, the second rotation-preventing member is provided as a pin and is fixedly mounted on an end surface of the second bearing housing facing the bearing body, and the bearing body is provided with a corresponding fifth accommodating hole.

Furthermore, the second rotation-preventing component is arranged to be a pin or a dowel, the second rotation-preventing component is installed along the radial direction of the second bearing shell from the periphery of the second bearing shell, one end of the second rotation-preventing component is fixed to the second bearing shell, the other end of the second rotation-preventing component is inserted into the periphery of the bearing body, and the periphery of the bearing body is provided with a corresponding sixth accommodating hole.

Furthermore, the second anti-rotation component is arranged as a key and is fixedly arranged on the end surface of the bearing body or is integrally formed with one end surface of the bearing body, and a corresponding third key groove is formed in the second bearing shell;

or the second anti-rotation component is a key and is fixedly installed on the inner diameter surface of the second bearing shell or integrally formed with the inner diameter surface of the second bearing shell, and the bearing body is provided with a corresponding fourth key groove.

Furthermore, the second anti-rotation component is arranged as a spherical body and fixedly installed on the end surface of the bearing body, and a corresponding third hemispherical groove is formed in the second bearing shell;

or the second rotation-preventing component is a spherical body and is fixedly installed on the end surface of the second bearing shell facing the bearing body, and the bearing body is provided with a corresponding fourth hemispherical groove.

According to another aspect of the present invention, a rotor system is provided, comprising the above-mentioned radial 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:

1. 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 pivot rotational speed, the dependable performance, long service life, and simple structure.

2. The utility model discloses a prevent changeing the form of component various, simple structure, it is with low costs, be convenient for realize.

3. The utility model discloses an air bearing structure that rotor system and miniature gas turbine applied and provided can carry out reliable and stable high-speed operation.

Drawings

Fig. 1 is a structural view of an anti-rotation member according to an embodiment of the present invention.

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

Fig. 3 is a structural view of a second anti-rotation member according to an embodiment of the present invention.

Fig. 4 is a cross-sectional view taken along a-a in fig. 3.

Fig. 5 is a structural diagram of a rotation preventing member according to an embodiment of the present invention.

Fig. 6 is a cross-sectional view taken along line a-a of fig. 5.

Fig. 7 is a structural diagram of a four rotation prevention member according to an embodiment of the present invention.

Fig. 8 is a cross-sectional view taken along line a-a of fig. 7.

Fig. 9 is a structural diagram of a five-rotation prevention member according to an embodiment of the present invention.

Fig. 10 is a cross-sectional view taken along line a-a of fig. 9.

Fig. 11 is a structural view of a sixth anti-rotation member according to an embodiment of the present invention.

Fig. 12 is a cross-sectional view taken along line a-a of fig. 11.

Fig. 13 is a structural diagram of a seventh rotation prevention member according to an embodiment of the present invention.

Fig. 14 is a cross-sectional view taken along line a-a of fig. 13.

Fig. 15 is a structural view of an eighth anti-rotation member according to an embodiment of the present invention.

Fig. 16 is a cross-sectional view taken along line a-a of fig. 15.

Fig. 17 is a structural view of a ninth rotation preventing member according to an embodiment of the present invention.

Fig. 18 is a cross-sectional view taken along line a-a of fig. 17.

Fig. 19 is a structural view of a tenth rotation preventing member according to an embodiment of the present invention.

Fig. 20 is a cross-sectional view taken along line a-a of fig. 19.

Fig. 21 is a structural view of an eleventh anti-rotation member according to the embodiment of the present invention.

Fig. 22 is a cross-sectional view taken along line a-a of fig. 21.

Fig. 23 is a structural view of a twelve rotation preventing member according to an embodiment of the present invention.

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

Fig. 25 is a view showing another structure of the thrust bearing of the present invention.

Fig. 26 is a front view of the present invention with an annular groove air bearing structure.

Fig. 27 is a cross-sectional view taken along line a-a of fig. 26.

Fig. 28 is a partially enlarged view of a bearing orifice according to the present invention.

Fig. 29 is a first structural view of the rotor system of the present invention.

Fig. 30 is a second structure diagram of the rotor system of the present invention.

Fig. 31 is a schematic structural view of a first air tank according to the present invention.

Fig. 32 is a schematic view of the radial bearing assembly of the present invention.

Fig. 33 is a schematic structural view of a second air tank according to the present invention.

Fig. 34 is a structure diagram of the second air tank assembly of the present invention.

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.

To an aspect of the present invention, an anti-rotation radial air bearing is provided.

The utility model discloses a prevent rotating radial air bearing 200 is used for installing pivot 110 to radially support pivot 110. The anti-rotation radial air 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 covers 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 the present invention, 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.

Example one

As shown in fig. 1 and 2, 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.

Example two

As shown in fig. 3 and 4, 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.

EXAMPLE III

As shown in fig. 5 and 6, 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.

Example four

As shown in fig. 7 and 8, in the present embodiment, the second rotation-preventing member 250 is configured 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 slot 232, so that the circumferential positioning of the bearing body 220 is realized by the key.

EXAMPLE five

As shown in fig. 9 and 10, 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.

EXAMPLE six

As shown in fig. 11 and 12, 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 realized by the spherical body.

EXAMPLE seven

As shown in fig. 11 and 12, in the present embodiment, the second anti-rotation member 250 may be provided with a spherical body and fixedly mounted on an 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 circumferential positioning of the bearing body 220 is achieved 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 utility model also provides an use above-mentioned radial air bearing's rotor system and miniature gas turbine, have the advantage that the operation is stable, dependable performance, long service life.

In the embodiment of the utility model provides an in, still provide a thrust air bearing who prevents rotating.

The utility model discloses a prevent rotating thrust air bearing 100 is used for installing pivot 110 to support pivot 110 in the axial. 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 the present invention, one end of the first rotation-preventing member 170 is fixedly connected to or integrally formed with the first bearing housing 150, and the other end of the first rotation-preventing member 170 is detachably connected to 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.

Example eight

As shown in fig. 13 and 14, 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.

Example nine

As shown in fig. 15 and 16, 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.

Example ten

As shown in fig. 17 and 18, 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.

EXAMPLE eleven

As shown in fig. 19 and 20, 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.

Example twelve

As shown in fig. 21 and 22, in the present embodiment, the first rotation-preventing member 170 is configured 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.

EXAMPLE thirteen

As shown in fig. 23 and 24, 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, and circumferential positioning of the bearing stator 180 is achieved by the spherical body.

Example fourteen

As shown in fig. 23 and 24, 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 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 stator and can prevent the bearing stator from rotating along the circumferential direction belongs to the protection scope of the present invention.

The utility model discloses a thrust air bearing is suitable for high-speed and the rotatory rotor system of hypervelocity, perhaps the great rotor system of diameter of axle, and at the operation in-process of rotor, bearing stator job stabilization can not take place to rotate along with the improvement of pivot 110 and thrust disc 120 rotational speed, the dependable performance, long service life, and simple structure.

In the embodiment of the present invention, a thrust bearing 100 structure is further provided. As shown in fig. 25, 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 forming a bearing stator 180, the second thrust disk 121 and the first thrust disk 122 forming 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, 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. The first anti-rotation member 170 provided in the above embodiment of the present invention is also applicable to the above thrust bearing structure of this embodiment.

In the embodiment of the utility model provides an in, still provide a radial bearing structure. As shown in fig. 26, 27 and 28, the radial bearing includes a second bearing housing 230 and a bearing body 220 that are sequentially nested from outside to inside, the rotating shaft 110 is disposed in the bearing body 220, and a second rotation-preventing member 250 is disposed between the second bearing housing 230 and the bearing body 220. The bearing body 220 is an annular cylinder, the bearing body 220 is radially provided with an orifice 270, the orifice 270 is a variable diameter hole, the aperture diameter of the orifice 270 on the outer wall of the bearing body 220 is larger than that of the orifice 270 on the inner wall, the inner wall of the bearing body 220 is circumferentially provided with an annular groove 260, and the orifice 270 on the inner wall is partially or integrally intersected with the annular groove 260.

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 above bearing structure provided by the present invention, because the throttle 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 shaft will not be worn to the throttle hole 270 in the annular groove 260, so as to prevent the throttle hole from being blocked, thereby improving the pneumatic lubrication effect; 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 utility model provides an in, still provide a rotor system who uses above-mentioned thrust bearing and journal bearing.

As shown in fig. 29, 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. 30, 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. 29, 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. 30, 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 rotor system of the present embodiment includes 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 flow 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.

Specifically, the first air groove 800 is provided in the end surface of the second stator 140 facing the second thrust disk 121 or the end surface of the second thrust disk 121 facing the second stator 140, and the first air groove 800 is provided in the end surface of the first stator 130 facing the first thrust disk 122 or the end surface of the first thrust disk 122 facing the first stator 130. The utility model discloses an among the above-mentioned rotor system, as shown in fig. 31, first air groove 800 is the arc wall, arc wall circumference equipartition and central symmetry, arc wall one end is adjacent with the centre of a circle, and the other end is adjacent with the circumference or intersects.

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 rotor system, 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 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 rotor system of the present embodiment. As shown in fig. 32, the radial bearing includes a bearing body 220, and a second air groove 900 is provided in a circumferential surface of the rotating shaft 110 corresponding to a position where the bearing body 220 is mounted or in a circumferential direction in an inner wall of the bearing body 220. 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. 33, 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. 34, 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 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 (8)

1. A radial air bearing for mounting to a rotating shaft to radially support the rotating shaft, comprising:

the bearing comprises a bearing body, a second bearing shell, a second bearing end cover and a second anti-rotation component;

the bearing body is sleeved on the rotating shaft, a preset gap is kept between the bearing body and the rotating shaft, the second bearing shell is covered on one axial end face and the periphery of the bearing body, and the second bearing end cover is sleeved on the rotating shaft and abutted against one end face of the second bearing shell;

the second rotation-preventing member is disposed between the second bearing housing and the bearing body and connects the second rotation-preventing member and the bearing body to fix the bearing body in the circumferential direction.

2. The radial air bearing of claim 1, wherein one end of the second anti-rotation member is fixedly connected or integrally formed with the second bearing housing, and the other end of the second anti-rotation member is detachably connected with the bearing body;

or one end of the second anti-rotation component is detachably connected with the second bearing shell, and the other end of the second anti-rotation component is fixedly connected with the bearing body or integrally formed.

3. The radial air bearing of claim 1, wherein the second anti-rotation member is configured as a pin and fixedly mounted to the end surface of the bearing body, and the second bearing housing is provided with a corresponding fourth receiving hole;

or, the second rotation-preventing member is provided as a pin and is fixedly mounted on an end surface of the second bearing housing facing the bearing body, and the bearing body is provided with a corresponding fifth accommodating hole.

4. The radial air bearing of claim 1, wherein the second rotation-preventing member is provided as a pin or a dowel, the second rotation-preventing member is installed from an outer circumference of the second bearing housing in a radial direction of the second bearing housing, one end of the second rotation-preventing member is fixed to the second bearing housing, the other end thereof is inserted into an outer circumference of the bearing body, and the outer circumference of the bearing body is provided with a corresponding sixth receiving hole.

5. The radial air bearing of claim 1, wherein the second anti-rotation member is configured as a key and is fixedly mounted to an end surface of the bearing body or is integrally formed with one end surface of the bearing body, and a corresponding third keyway is provided on the second bearing housing;

or the second anti-rotation component is a key and is fixedly installed on the inner diameter surface of the second bearing shell or integrally formed with the inner diameter surface of the second bearing shell, and the bearing body is provided with a corresponding fourth key groove.

6. The radial air bearing of claim 1, wherein the second anti-rotation member is provided as a spherical body and fixedly mounted to an end surface of the bearing body, and a corresponding third semi-spherical groove is provided in the second bearing housing;

or the second rotation-preventing component is a spherical body and is fixedly installed on the end surface of the second bearing shell facing the bearing body, and the bearing body is provided with a corresponding fourth hemispherical groove.

7. A rotor system comprising a radial air bearing according to any of claims 1 to 6.

8. A micro gas turbine comprising the rotor system of claim 7.

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