CN208858777U - A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system - Google Patents
A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system Download PDFInfo
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- CN208858777U CN208858777U CN201821612816.XU CN201821612816U CN208858777U CN 208858777 U CN208858777 U CN 208858777U CN 201821612816 U CN201821612816 U CN 201821612816U CN 208858777 U CN208858777 U CN 208858777U
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Abstract
The utility model provides a kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system, wherein, bearing damp device is for being installed in non-contact type bearing, the bearing damp device is made of shape-memory material, and the bearing damp device can adjust the gap between the non-contact type bearing and shaft by plastic deformation.In the utility model, by the way that bearing damp device is arranged in non-contact bearing, the bearing clearance between stationary parts and rotary part is adjusted and is corrected using the plastic deformation of bearing damp device itself to realize.In this way, so that the requirement of bearing machining precision and assembly precision reduces, and to keep more stable cooperation precision between the stationary parts of bearing and rotary part by being provided with above-mentioned bearing damp device within the bearing.
Description
Technical field
The utility model relates to technical field of bearings more particularly to a kind of bearing damp device, transverse bearing, thrust bearing and
Rotor-support-foundation system.
Background technique
Non-contact type bearing is due to the features such as its coefficient of friction and moment of friction are small, kinematic accuracy is high, in some high revolving speeds
Occasion using more and more common.But compared to the mechanical bearing of contact, the bearing clearance very little of non-contact type bearing adds
Work difficulty is higher.
For example, the bearing clearance between bearing inner race and shaft is very narrow for contactless transverse bearing, this is just
It is required that shaft and bearing inner race all have very high machining accuracy and assembly precision, otherwise it is easy to generate and touches axis phenomenon, to axis
Manufacture into abrasion and damage.Likewise, the bearing clearance for contactless thrust bearing, between stator and thrust disc
It is very narrow, therefore it is required that stator and thrust disc all have very high machining accuracy and assembly precision, to prevent fastening and thrust disc
Between generate collision and abrasion.
Utility model content
The utility model provides a kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system, to solve above-mentioned ask
Topic.
In a first aspect, the utility model provides a kind of bearing damp device, the bearing damp device is non-contact for being installed on
In formula bearing, the bearing damp device is made of shape-memory material, and the bearing damp device can be adjusted by plastic deformation
Bearing clearance between stationary parts and rotary part.
Second aspect, the utility model provide a kind of transverse bearing, and for being installed on shaft, the radial axle is contracted
It includes:
Bearing body；
The bearing inner race being sheathed in the bearing body, the bearing inner race and the shaft that is sheathed in bearing inner race it
Between have bearing clearance；
And it is set to the bearing damp device between the bearing inner race and the bearing body, the bearing damp device
For bearing damp device described in first aspect, under the action of the bearing inner race plasticity can occur for the bearing damp device
Deformation, to adjust the bearing clearance.
The third aspect, the utility model provide a kind of thrust bearing, and for being installed on shaft, the thrust axis is contracted
It includes:
Thrust disc, the thrust disc are connected in the shaft；
And it is arranged in the first stator and the second stator in the shaft, first stator and second stator
It is respectively arranged at the opposite sides of the thrust disc；
In first stator and second stator, each stator includes institute in stator body, pressing plate and first aspect
The bearing damp device stated, the bearing damp device are set between the stator body and the pressing plate, and the pressing plate is set to
The side close to the thrust disc of the stator body, has bearing clearance between the pressing plate and the thrust disc；
Wherein, the bearing damp device can be plastically deformed under the action of the pressing plate, to adjust the bearing
Gap.
Fourth aspect, the utility model provide a kind of rotor-support-foundation system, including shaft, thrust bearing and at least two radial axles
Hold, the thrust bearing and at least two transverse bearing are mounted in the shaft, the thrust bearing and it is described extremely
Few two transverse bearings are non-contact type bearing；
Wherein, at least one transverse bearing at least two transverse bearing is radial axle described in second aspect
It holds；And/or the thrust bearing is thrust bearing described in the third aspect.
In the utility model, by the way that bearing damp device is arranged in non-contact bearing, to realize using bearing damp device certainly
The plastic deformation of body is adjusted and corrects to the bearing clearance between stationary parts and rotary part.In this way, by bearing
In be provided with above-mentioned bearing damp device so that the requirement of bearing machining precision and assembly precision reduces, and make the static of bearing
More stable cooperation precision is kept between component and rotary part.
Detailed description of the invention
In order to illustrate more clearly of the technical solution of the utility model embodiment, the utility model embodiment will be retouched below
Attached drawing needed in stating is briefly described, it should be apparent that, the accompanying drawings in the following description is only the utility model
Some embodiments for those of ordinary skill in the art without any creative labor, can be with root
Other attached drawings are obtained according to these attached drawings.
Fig. 1 is a kind of one of the structural schematic diagram of bearing damp device；
Fig. 2 is a kind of second structural representation of bearing damp device；
Fig. 3 is the structural schematic diagram of transverse bearing；
Fig. 4 be in Fig. 3 A-A to cross-sectional view；
Fig. 5 is a kind of structural schematic diagram of dynamic pressure generation trough of transverse bearing；
Fig. 6 is the structural schematic diagram of another dynamic pressure generation trough of transverse bearing；
Fig. 7 is the structural schematic diagram of thrust bearing；
Fig. 8 is a kind of structural schematic diagram of dynamic pressure generation trough of thrust bearing；
Fig. 9 is the structural schematic diagram of another dynamic pressure generation trough of thrust bearing；
Figure 10 to Figure 27 is the structural schematic diagram of various horizontal rotor systems provided by the embodiment of the utility model；
Figure 28 to Figure 45 is the structural schematic diagram of various vertical rotor systems provided by the embodiment of the utility model.
Specific embodiment
The following will be combined with the drawings in the embodiments of the present invention, carries out the technical scheme in the embodiment of the utility model
It clearly and completely describes, it is clear that the embodiments are a part of the embodiments of the present invention, rather than whole implementation
Example.Based on the embodiments of the present invention, those of ordinary skill in the art are obtained without creative efforts
The every other embodiment taken, fall within the protection scope of the utility model.
In a first aspect, the utility model embodiment provides a kind of bearing damp device, as shown in Figure 1 to Figure 2, the bearing damp
Device is used to be installed in non-contact type bearing, such as contactless transverse bearing, contactless thrust bearing etc..The axis
It holds damper to be made of shape-memory material, which can pass through plastic deformation adjustment stationary parts and rotary part
Between bearing clearance.
In the utility model embodiment, realized by the plastic deformation of bearing damp device itself to stationary parts and rotating part
Bearing clearance between part is adjusted and corrects, so that the requirement of bearing machining precision and assembly precision reduces.Due to
Bearing damp device is made of shape-memory material, therefore, after bearing damp device generates plastic deformation, the shape of bearing damp device
It will remain unchanged, so that keeping more stable cooperation precision between the stationary parts and rotary part of bearing.
The bearing damp device of the utility model embodiment can be used for transverse bearing, can be used for thrust bearing.
When bearing damp device is used for transverse bearing, bearing damp device can pass through plastic deformation adjustment transverse bearing and shaft
Between bearing clearance, at this moment, stationary parts is transverse bearing, and rotary part is the shaft being sheathed in transverse bearing.Bearing
When damper is used for transverse bearing, the concentricity between transverse bearing and shaft can be corrected, reduce transverse bearing and shaft
Machining accuracy and assembly precision reduce the generation for touching axis phenomenon.
When bearing damp device is used for thrust bearing, bearing damp device can pass through the stator of plastic deformation adjustment thrust bearing
Bearing clearance between thrust disc, at this moment, stationary parts are the stator of thrust bearing, and rotary part is the thrust of thrust bearing
Disk.When bearing damp device is used for thrust bearing, the depth of parallelism between the thrust disc of thrust bearing and stator can be corrected, so as to
To reduce the machining accuracy and assembly precision of the thrust disc and stator of thrust bearing in flatness.
It is used for the specific embodiment of transverse bearing and thrust bearing about bearing damp device, will carry out hereinafter specifically
It is bright.
Bearing damp device can be made of shape memory metal or shape-memory polymer, wherein shape memory metal can
Think any one in Ti-Ni alloy, ormolu, Batterium, copper-molybdenum nickel alloy and copper gold kirsite.If bearing
Working environment is hot environment, then the shape memory metal of high temperature resistant (such as 300 DEG C or more) may be selected in bearing damp device 530.
It should be noted that make bearing damp device generate the power resources of plastic deformation in non-contact type bearing and shaft it
Between gas film pressure, the collective effect power to Bearing inner part of shaft gravity and shaft load.Below in conjunction with different axis
It holds and is specifically described respectively.
In the utility model embodiment, bearing damp device may include at least two adjustment units 531, and bearing damp device can
Think that the integral device of formation is continuously arranged in above-mentioned at least two adjustment unit, also may include at least two tune being independently arranged
Whole component, the adjustment member may include at least one adjustment unit 531, for example, an adjustment unit 531 is an adjustment structure
Part, two adjustment units 531 form an adjustment member, and three adjustment units 531 form adjustment member, etc..It can be with
Understand, when an adjustment unit 531 forms an adjustment member, adjustment unit 531 is equal to adjustment member.Work as bearing
When damper is that the integral device of formation is continuously arranged at least two adjustment units, on the one hand, during installation can be more quick；
On the other hand, the bearing of different sizes or type may need to configure different types of bearing damp device, and the scope of application is more
Limitation.When bearing damp device includes the adjustment member that at least two are independently arranged, the adjustment member being independently arranged can be applicable in
In any bearing, it is only necessary to according to the size of bearing or the appropriate number of adjustment member of Specific disposition, or by multiple adjustment structures
Part arrangement is the shape suitable for bearing.
In the utility model embodiment, adjustment unit 531 can be half shell structure, including lug boss 532 and support portion
533, lug boss 532 and support portion 533 are integrally formed.The outer surface of the lug boss 532 is smooth arc-shaped curved surface, the support portion
533 stretch from lug boss 532 is smooth around.Entire adjustment unit 531 can be produced using lug boss 532 as adjustment unit 531
The position of raw plastic deformation, support portion 533 can be used as the position for supporting entire adjustment unit 531.Adjustment unit 531 is arranged
For above-mentioned half shell structure, so that adjustment unit 531 is in more stable state before and after stress.
Other than above-mentioned half shell structure, adjustment unit 531 can also be wavy shaped configuration, zigzag structure, spherical shell
Structure, hemisphere shell structure etc..
In the utility model embodiment, in order to make adjustment unit 531 that there is preferable plastically deformed performance, adjustment unit
531 thickness should not be too large；In order to make adjustment unit 531 have more stable mechanical property, the height of adjustment unit 531 is unsuitable
It is excessive.The height H of adjustment unit 531 can be 1mm between 3mm, and the thickness L of adjustment unit 531 can be for 0.1mm extremely
Between 0.3mm.
In the utility model embodiment, by the way that bearing damp device is arranged in non-contact bearing, hindered with realizing using bearing
The plastic deformation of Buddhist nun's device itself is adjusted and corrects to the bearing clearance between stationary parts and rotary part.In this way, passing through
It is provided with above-mentioned bearing damp device within the bearing, so that the requirement of bearing machining precision reduces, and makes the stationary parts of bearing
More stable cooperation precision is kept between rotary part.Also, above-mentioned bearing damp device structure is simple, production and processing is convenient,
The structure of original bearing is had no need to change, widespread adoption is suitable for.
Second aspect, the utility model embodiment provide a kind of transverse bearing, as shown in Figures 3 to 6, transverse bearing 500,
For being installed on shaft 100, transverse bearing 500 includes:
Bearing body 520；
The bearing inner race 540 being sheathed in shaft 100 has bearing clearance, axis between bearing inner race 540 and shaft 100
It holds inner ring 540 to be sheathed in bearing body 520, and can be moved in bearing body 520；
And it is set to the bearing damp device 530 between bearing inner race 540 and bearing body 520, the bearing damp device
530 can be affixed setting with the aperture surface of bearing body 520, which is made of shape-memory material, the bearing
Damper 530 can be plastically deformed under the action of bearing inner race 540, to adjust bearing clearance.
In the utility model embodiment, transverse bearing 500 is installed in shaft 100, after the starting of shaft 100, radial axle
The bearing inner race 540 for holding 500 adjusts itself position under the collective effect of gas film pressure, shaft gravity and shaft load, with
The bearing clearance between shaft 100 and bearing inner race 540 is set to meet the needs of bearing steadily operates.In this way, transverse bearing 500 with
Cooperation precision between shaft 100, i.e. concentricity are adjusted or correct.
In above process, corresponding plasticity has occurred under the squeezing action of bearing inner race 540 and becomes for bearing damp device 530
Shape, and then bearing inner race 540 is supported on to new equilbrium position, complete the tune of concentricity between shaft 100 and bearing inner race 540
Whole or correction is caused to wear and be damaged to avoid shaft 100 to bearing inner race 540.
As previously mentioned, bearing damp device 530 may include at least two adjustment units 531, bearing damp device can be upper
The integral device that formation is continuously arranged at least two adjustment units is stated, also may include at least two adjustment structures being independently arranged
Part, the adjustment member may include at least one adjustment unit 531.
As previously mentioned, adjustment unit 531 is half shell structure, including lug boss 532 and support portion 533, lug boss 532 with
Support portion 533 is integrally formed；The lug boss 532 is towards bearing inner race 540, the aperture surface phase of support portion 533 and bearing body 520
It is sticked and sets；The lug boss 532 can be plastically deformed under the action of bearing inner race 540, to adjust bearing clearance, i.e. bearing
Gap between inner ring 540 and shaft 100.
Shaft 100 starting after the bearing initial operation stage, bearing inner race 540 move radially or axis upwards about
Axis oscillating certain angle, to adjust the concentricity of shaft 100 Yu bearing inner race 540, until reaching the steady operating condition of bearing.
During above-mentioned adjustment, since adjustment unit 531 is made of memory metal, it is extruded the protrusion of the adjustment unit 531 of side
Portion 532 is pressurized and is plastically deformed, and is maintained at the deformation state.Radial direction can be corrected by adjusting the deformation of unit 531
Concentricity between bearing and shaft, so as to reduce the machining accuracy and assembly precision of bearing inner race 540 and shaft 100,
Reduce the generation for touching axis phenomenon.
As previously mentioned, the height H of adjustment unit 531 can be 1mm between 3mm, the thickness L of adjustment unit 531 can be with
It is 0.1mm between 0.3mm.
In the utility model embodiment, adjustment member can be circumferentially evenly distributed with along the aperture surface of bearing body 520, be formed annular in shape
The bearing damp device 530 of arrangement；Adjustment member can be also axially evenly distributed with along the aperture surface of bearing body 520, formed and arranged in line style
Bearing damp device 530；Adjustment member can be also circumferentially evenly distributed with along the aperture surface of bearing body 520, and along bearing body 520
Diametric plane is axially uniformly distributed, forms the bearing damp device 530 in polycyclic arrangement.The set-up mode of above-mentioned adjustment member can make bearing
The adjustment process in gap is more steady, so that bearing clearance is more uniform.
It, can be in the corresponding installation diameter of shaft 100 before transverse bearing 500 operates for the first time in the utility model embodiment
Protective layer is set to the position of bearing 500, to protect the mating surface of shaft 100 and transverse bearing 500.Specifically, can be in shaft
Protective layer is arranged in the both ends of the position of 100 corresponding installation transverse bearing 500.In this way, in the starting of shaft 100 or calibration phase,
It rubs between protective layer elder generation and bearing inner race 540, to play protection to the mating surface of shaft 100 and bearing inner race 540
Effect.The protective layer can be set using the materials such as Te Folun, graphite, babbit, the protective layer by the way of coating
It is placed in shaft 100.
Transverse bearing 500 in the utility model embodiment can be hydrodynamic gas-lubricated bearing, hydrostatic gas-lubricated bearing, dynamic and static pressure
Any one of gas bearing such as mixed gas bearing.
When transverse bearing 500 is hydrodynamic gas-lubricated bearing, the aperture surface of bearing inner race 540 or shaft 100 are towards in bearing
Dynamic pressure generation trough 541 is provided on the periphery of circle 540.
The dynamic pressure generation trough 541 can be formed by forging, rolling, etching or punching press.For convenient for dynamic pressure generation trough 541
Processing, bearing inner race 540 can be made of stainless steel material.When shaft 100 is relative to 540 high-speed rotation of bearing inner race,
Air hydrodynamic is generated in dynamic pressure generation trough 541, shaft 100 is made to float.Wherein, the angle of the servo-actuated pressure generation trough 541 of the amount of floating
Degree, groove width, slot number, length, the difference of depth and flatness and change.In addition, the air generated in dynamic pressure generation trough 541 is dynamic
The size of pressure is also related with the rotation speed of shaft 100 and bearing clearance.It can be according to actual condition to dynamic pressure generation trough 541
Parameter be designed.
The middle section of the periphery of corresponding shaft bearing inner ring 540 in shaft 100 can be set in dynamic pressure generation trough 541,
It can be set to be symmetrically distributed in the two sides of middle section, mutually independent two parts dynamic pressure generation trough 541；Dynamic pressure generation trough
541 can also be arranged in the middle section of 540 aperture surface of bearing inner race, may be set to be and are symmetrically distributed in bearing inner race 540
Aperture surface both ends, mutually independent two parts dynamic pressure generation trough 541.
In the utility model embodiment, dynamic pressure generation trough 541 can arrange in matrix.In this way, being conducive to make air film more evenly
Ground is distributed in bearing clearance.
In the utility model embodiment, dynamic pressure generation trough 541 can be continuous or spaced V-shaped groove.In such manner, it is possible to
In the case that shaft 100 is rotated in the forward direction or reversely rotated, shaft 100 can be kept in a non-contact manner in the desired manner, from
And shaft 100 is made to have the advantages that high load capacity and stability are good.Dynamic pressure generation trough 541, can be in addition to being set as V-shaped groove
It is set as man type chute or other shapes of slot.
When transverse bearing 500 is hydrostatic gas-lubricated bearing, transverse bearing is additionally provided with connection bearing clearance and external gas source
Static pressure air inlet restriction hole 521, static pressure air inlet restriction hole 521 is for external gas source to be delivered in bearing clearance.The static pressure into
The circulation diameter of moral discharge orifice 521 can be adjusted according to actual conditions such as tolerance demands.
In the utility model embodiment, static pressure air inlet restriction hole 521 is in turn through bearing body 520, bearing damp device
530 and bearing inner race 540, bearing clearance is connected to external gas source.
In the utility model embodiment, static pressure air inlet restriction hole 521 is divided at least two branches company in transverse bearing 500
It passes in bearing clearance.In such manner, it is possible to keep the gas film pressure in the bearing clearance of transverse bearing 500 more uniform.Wherein, static pressure
The circulation diameter of air inlet restriction hole 521 and each branch can be adjusted according to actual conditions such as tolerance demands.
When transverse bearing 500 is hybrid gas bearing, which had both been provided with dynamic pressure generation trough
541, it is also equipped with static pressure air inlet restriction hole 521.Due to aforementioned respectively to dynamic pressure generation trough 541 and static pressure air inlet restriction hole
521 are illustrated, and to avoid repeating, details are not described herein again.
The transverse bearing 500 of the utility model embodiment can also be gas magnetic combined bearing, i.e., in any of the above-described kind of gas
On the basis of bearing, it is provided with multiple magnetic parts on bearing body 520, magnetic portion can also be correspondingly set in shaft 100
Part, in this way, shaft 100 can under the magneticaction of multiple magnetic parts moving in the radial direction in shaft 100.
The third aspect, the utility model embodiment provide a kind of thrust bearing, as shown in Figure 7 to 9, thrust bearing 700,
For being installed on shaft 100, thrust bearing 700 includes:
Thrust disc 710, thrust disc 710 are connected in shaft 100；
And it is arranged in the first stator 720 and the second stator 730 in shaft 100, the first stator 720 and the second stator
730 are respectively arranged at the opposite sides of thrust disc 710；
In first stator 720 and the second stator 730, each stator includes stator body, pressing plate and bearing damp device 530,
Bearing damp device 530 is set between stator body and pressing plate, and pressing plate is set to the side of the close thrust disc of stator body, pressure
There is bearing clearance between plate and thrust disc 710；
Wherein, which is made of shape-memory material, and bearing damp device 530 can be in the effect of pressing plate
It is lower to be plastically deformed, to adjust bearing clearance.
Specifically, the first stator 720 includes the first stator body 722, bearing damp device 530 and the first pressing plate 723, the
The end face towards thrust disc 710 of one stator body 722 is equipped with bearing damp device 530, is close to the bearing damp device 530 installation
There is the first pressing plate 723；Second stator 730 includes the second stator body 732, bearing damp device 530 and the second pressing plate 733, the
The end face towards thrust disc 710 of two stator bodies 732 is equipped with bearing damp device 530, is close to the bearing damp device 530 installation
There is the second pressing plate 733.
The bearing initial operation stage after the starting of shaft 100, the first pressing plate 723 and the second pressing plate 733 gas film pressure,
The position of itself is adjusted under the collective effect of the axial load of shaft 100, so that the first stator 720, the second stator 730 and thrust
Gap between disk 710 meets the needs of bearing steadily operates.In the process, bearing damp device 530 in the first pressing plate 723 or
Corresponding plastic deformation occurs under the squeezing action of second pressing plate 733, and then the first pressing plate 723 and the second pressing plate 733 are supported
In new equilbrium position, the correction of the depth of parallelism between thrust disc 710 and the first stator 720, the second stator 730 is completed, to avoid
Abrasion and collision between thrust disc 710 and the first stator 720, the second stator 730.Thrust bearing 700 is just completed in this way
Cooperation precision between thrust disc 710 and the first stator 720, the second stator 730, the i.e. correction of the depth of parallelism.
As previously mentioned, bearing damp device 530 may include at least two adjustment units 531, bearing damp device can be upper
The integral device that formation is continuously arranged at least two adjustment units is stated, also may include at least two adjustment structures being independently arranged
Part, the adjustment member may include at least one adjustment unit 531.
As previously mentioned, adjustment unit 531 is half shell structure, including lug boss 532 and support portion 533, lug boss 532 with
Support portion 533 is integrally formed.For the first stator 720, the lug boss 532 towards the first pressing plate 723, support portion 533 with
First stator body 722 is affixed setting；For the second stator 730, the lug boss 532 is towards the second pressing plate 733, support portion
533 and second stator body 732 be affixed setting.The lug boss 532 can be in the effect of the first pressing plate 723 or the second pressing plate 733
It is lower to be plastically deformed, to adjust bearing clearance.
In the bearing initial operation stage after the starting of shaft 100, the first pressing plate 723 or the second pressing plate 733 move in the axial direction
It is dynamic or around axis oscillating certain angle, it is parallel between thrust disc 710 and the first stator 720, the second stator 730 to adjust
Degree, until reaching the steady operating condition of bearing.During above-mentioned adjustment, since adjustment unit 531 is made of memory metal, quilt
The compression of lug boss 532 for squeezing the adjustment unit 531 of side is plastically deformed, and is maintained at the deformation state.Pass through tune
The deformation of whole unit 531 can correct the depth of parallelism between thrust disc 710 and the first stator 720, the second stator 730, so as to
To reduce the machining accuracy and assembly precision of thrust disc 710, the first stator 720 and the second stator 730 in flatness.
As previously mentioned, the height H of adjustment unit 531 can be 1mm between 3mm, the thickness L of adjustment unit 531 can be with
It is 0.1mm between 0.3mm.
In the utility model embodiment, adjustment member can be respectively along the first stator body 722 and the second stator body 732
End face is circumferentially uniformly distributed, forms the bearing damp device 530 annularly arranged；Adjustment member can also be respectively along the first stator body 722
With the end face radial equipartition of the second stator body 732, the bearing damp device 530 in line style arrangement is formed；Adjustment member can also divide
It is circumferentially not uniformly distributed along the end face of the first stator body 722 and the second stator body 732, and respectively along 722 He of the first stator body
The end face radial equipartition of second stator body 732, so that adjustment member is respectively along the first stator body 722 and the second stator body
Multi-turn is distributed in 732 end face, forms the bearing damp device 530 in polycyclic arrangement.The set-up mode of above-mentioned adjustment member
So that the adjustment process of bearing clearance is more steady, so that bearing clearance is more uniform.
Thrust bearing 700 in the utility model embodiment can be hydrodynamic gas-lubricated bearing, hydrostatic gas-lubricated bearing, dynamic and static pressure
Any one of gas bearing such as mixed gas bearing.
When thrust bearing 700 is hydrodynamic gas-lubricated bearing, the end face towards thrust disc 710 of pressing plate or thrust disc 710
Dynamic pressure generation trough 741 is provided on towards the end face of pressing plate.For the first stator 720, the first pressing plate 723 towards thrust
Dynamic pressure generation trough 741 is provided on the end face of the first pressing plate 723 of direction of the end face or thrust disc 710 of disk 710；It is fixed for second
For son 730, the end face of the second pressing plate 733 of direction of the end face or thrust disc 710 towards thrust disc 710 of the second pressing plate 733
On be provided with dynamic pressure generation trough 741.
The dynamic pressure generation trough 741 can be formed by forging, rolling, etching or punching press.For convenient for dynamic pressure generation trough 741
Processing, the first pressing plate 723 and the second pressing plate 733 can be made of stainless steel material.In 710 high-speed rotation of thrust disc, deposit
It is that the flowing gas of bearing clearance is pressed into dynamic pressure generation trough 741, so that pressure is generated, to realize thrust disc 710 along axis
It is non-contactly kept to direction.Wherein, dynamic pressure generation trough 741 generates the angle of the servo-actuated pressure generation trough 741 of size of pressure, slot
Width, slot number, length, the difference of depth and flatness and change.In addition, the air hydrodynamic generated in dynamic pressure generation trough 741
Size is also related with the rotation speed of thrust disc 710 and bearing clearance.It can be according to actual condition to dynamic pressure generation trough 741
Parameter is designed.
In the utility model embodiment, dynamic pressure generation trough 741 can radially or concentric circles are arranged.In this way, being conducive to
It is more evenly distributed in air film in bearing clearance.
In the utility model embodiment, dynamic pressure generation trough 741 may include the first helicla flute 7411 and the second helicla flute 7412,
First helicla flute 7411 is surrounded on outside the second helicla flute 7412, the spiral trend of the first helicla flute 7411 and the second helicla flute 7412
On the contrary, one end close to the second helicla flute 7412 of the first helicla flute 7411 is with the second helicla flute 7412 close to the first helicla flute
7411 one end connects or disconnects.
Wherein, the distance etc. in one end to the axle center of shaft 100 close to the second helicla flute 7412 of the first helicla flute 7411
In one end close to the second helicla flute 7412 of the first helicla flute 7411 to the first pressing plate 723 and the second pressing plate 733 or thrust disc
The distance of 710 neighboring.Alternatively, one end close to the first helicla flute 7411 of the second helicla flute 7412 is to shaft 100
The distance in axle center is equal to one end close to the first helicla flute 7411 of the second helicla flute 7412 to the first pressing plate 723 and the second pressing plate
733 or thrust disc 710 neighboring distance.
It, can be in shaft 100 by using the set-up mode of above-mentioned dynamic pressure generation trough 741 in the utility model embodiment
In the case where rotating in the forward direction or reversely rotating, thrust disc 710 can be kept in a non-contact manner in the desired manner, to make to turn
Axis 100 has the advantages that high load capacity and stability are good.
When thrust bearing 700 is hydrostatic gas-lubricated bearing, be additionally provided on the first stator 720 connection bearing clearance with it is external
First static pressure air inlet restriction hole 721 of gas source is additionally provided with the second of connection bearing clearance and external gas source on the second stator 730
Static pressure air inlet restriction hole 731.First static pressure air inlet restriction hole 721 and the second static pressure air inlet restriction hole 731 are respectively used to will be external
Gas source is delivered in bearing clearance.The circulation diameter in the first static pressure air inlet restriction hole 721 and the second static pressure air inlet restriction hole 731 can
To be adjusted according to actual conditions such as tolerance demands.
In the utility model embodiment, the first static pressure air inlet restriction hole 721 is in turn through the first stator body 722, axis
Damper 530 and the first pressing plate 723 are held, bearing clearance is connected to external gas source；Second static pressure air inlet restriction hole 731 can be successively
Across the second stator body 732, bearing damp device 530 and the second pressing plate 733, bearing clearance is connected to external gas source.
When thrust bearing 700 is hybrid gas bearing, which had both been provided with dynamic pressure generation trough
741, it is also equipped with the first static pressure air inlet restriction hole 721 and the second static pressure air inlet restriction hole 731.Due to aforementioned respectively to dynamic
Pressure generation trough 741, the first static pressure air inlet restriction hole 721 and the second static pressure air inlet restriction hole 731 are illustrated, to avoid repeating,
Details are not described herein again.
The thrust bearing 700 of the utility model embodiment can also be gas magnetic combined bearing, i.e., in any of the above-described kind of gas
On the basis of bearing, the first magnetic part is provided on thrust disc 710, in the first stator body 722 and the second stator body
Be additionally provided with multiple second magnetic parts in 732, thrust disc 710 can the first magnetic part and multiple second magnetic parts it
Between magneticaction under moved on the axial direction of shaft 100.
Fourth aspect, the utility model embodiment are provided in a kind of transverse bearing using in second aspect or the third aspect
Thrust bearing rotor-support-foundation system, which can be horizontal rotor system, is also possible to vertical rotor system.
In the utility model embodiment, a kind of rotor-support-foundation system, including shaft and at least two transverse bearings, at least two diameters
It is set in shaft to bearing holder (housing, cover), at least two transverse bearings are non-contact type bearing；
Wherein, at least one transverse bearing at least two transverse bearings is any radial axle that second aspect provides
It holds.
Optionally, the axis body of shaft is structure as a whole, and shaft is horizontally disposed or vertically arranged；
Motor, compressor and turbine are disposed in shaft；
Thrust bearing is additionally provided in shaft, thrust bearing is non-contact type bearing；
Wherein, thrust bearing is set on the predeterminated position of the side of the close compressor of turbine, and predeterminated position is can
The center of gravity of rotor-support-foundation system is set to be located at the position at least two transverse bearings between two transverse bearings of lie farthest away.
Further, the thrust bearing in the rotor-support-foundation system can be any thrust bearing that the third aspect provides.
In utility model embodiment, a kind of rotor-support-foundation system, any thrust bearing including shaft and third aspect offer,
Thrust bearing is installed in shaft.
Optionally, the axis body of shaft is structure as a whole, and shaft is horizontally disposed or vertically arranged；
Motor, compressor and turbine are disposed in shaft；
At least two transverse bearings are additionally provided in shaft, at least two transverse bearings are non-contact type bearing；
Wherein, thrust bearing is set on the predeterminated position of the side of the close compressor of turbine, and predeterminated position is can
The center of gravity of rotor-support-foundation system is set to be located at the position at least two transverse bearings between two transverse bearings of lie farthest away.
Further, the transverse bearing in the rotor-support-foundation system can be any transverse bearing that second aspect provides.
The numerous embodiments of horizontal rotor system presented below.
As shown in Figure 10, a kind of horizontal rotor system, including shaft 100, turbine 200, compressor 300, motor 400,
One transverse bearing 500, the second transverse bearing 600 and thrust bearing 700, it is radial that the shaft 100 passes through first set gradually
Bearing 500, thrust bearing 700, motor 400, compressor 300, the second transverse bearing 600 and turbine 200, the shaft 100 exist
Rotation in first transverse bearing 500, the stator of thrust bearing 700, the stator of motor 400 and the second transverse bearing 600, institute
It states shaft 100 to be fixedly connected with the compression wheel of the turbine of the thrust disc of thrust bearing 700 and turbine 200, compressor 300, root
According to entire horizontal rotor system (weight including motor 400), the quality and/or axial position of the thrust bearing 700 are adjusted,
It falls in the center of gravity of the entire rotor-support-foundation system between the first transverse bearing 500 and the second transverse bearing 600, preferably falls in and calm the anger
On machine 300.
As shown in figure 11, when the turbine weight of turbine is excessive, by the setting of thrust bearing 700 in 500 He of the first transverse bearing
When between motor 400, when entire horizontal rotor system gravity can not still be fallen between farthest two transverse bearings, then using implementation
Horizontal rotor system shown in example 2, the difference with horizontal rotor system described in embodiment 1 are only that the thrust bearing
700 further Forwards, positioned at the front end of the first transverse bearing 500 (wherein the direction of motor to turbine is from front to back).
Horizontal rotor system shown in Figure 10 to Figure 11 is suitable for the turbine turbine of heavy, and for example the material of turbine is gold
Belong to.
For the turbine turbine of lightweight, for example the material of turbine turbine is ceramic material, ceramic fibrous composite material etc., when
The diameter of the thrust disc of thrust bearing 700 is smaller, when will not block gas turbine inlet, is then turned using level as shown in figure 12
Subsystem, the difference with the horizontal rotor system shown in Figure 10 are only that the position for moving back thrust bearing 700, are located at electricity
Between machine 400 and compressor 300, and the diameter of the thrust disc of thrust bearing 700 is smaller, will not block gas turbine inlet.
For the stability for improving entire horizontal rotor system, changed in the horizontal rotor system shown in Figure 10 to Figure 12
Into.For the horizontal rotor system shown in Figure 10 and Figure 11, increase third transverse bearing between motor 400 and compressor 300
800, for the horizontal rotor system shown in Figure 12, between thrust bearing 700 and compressor 300 or in motor 400 and push away
Third transverse bearing 800 is set between power bearing 700, referring specifically to Figure 13 to Figure 16.
When motor weight is excessive, the center of gravity of entire rotor-support-foundation system can not be made to be located at farthest 2 diameters by the thrust bearing that moves forward
When between bearing, in the horizontal rotor system of original cantilever structure, cancels shaft coupling, set at entire rotor-support-foundation system both ends
Transverse bearing is set, makes entire rotor-support-foundation system in the spindle bodily form, so that entire rotor-support-foundation system stable structure, hair when avoiding high speed rotation
Raw unstability situation, meets the high-revolving requirement of current gas turbine, on this basis, since thrust bearing contains magnetic element
When, magnetic element can not be resistant to the high warm that turbine transmits, and increase a radial axle between thrust bearing 700 and turbine 200
It holds, so that thrust bearing 700 is not affected by high temperatures far from turbine 200, referring specifically to Figure 17.
As shown in figure 17, a kind of horizontal rotor system, including shaft 100, turbine 200, compressor 300, motor 400,
One transverse bearing 500, the second transverse bearing 600, thrust bearing 700 and the 4th transverse bearing 801, the shaft 100 pass through according to
The first transverse bearing 500, motor 400, compressor 300, thrust bearing 700, the second transverse bearing 600, turbine 200 of secondary setting
With the 4th transverse bearing 801, the shaft 100 is in first transverse bearing 500, the stator of motor 400, thrust bearing 700
Stator, rotation in the second transverse bearing 600 and the 4th transverse bearing 801, the thrust of the shaft 100 and thrust bearing 700
The turbine of disk and turbine 200, compressor 300 compression wheel be fixedly connected.
For the stability for improving entire horizontal rotor system, improved in the horizontal rotor system shown in Figure 17,
Increase third transverse bearing 800 between motor 400 and compressor 300, referring specifically to Figure 18.
Preferably, the first transverse bearing 500, the second transverse bearing 600 and third transverse bearing 800, the 4th transverse bearing
801 be untouchable transverse bearing.
Preferably, the second transverse bearing 600, the 4th transverse bearing 801 are externally pressurized air bearing and gas dynamic pressure diameter
The hybrid transverse bearing combined to bearing.
Preferably, the first transverse bearing 500 and third transverse bearing 800 are gas magnetic hybrid radial bearing.
Preferably, motor 400 is fluid dynamic bearing motor, and the part that motor 400 is corresponded in the shaft 100 is provided with
Dynamic pressure generation trough.
Preferably, turbine 200 is provided with heat-barrier material close to the end face of the second transverse bearing 600, for example aeroge.
Preferably, compressor 300 is centrifugal compressor.
Preferably, turbine turbine is centrifugal turbine.
Preferably, to be that externally pressurized air bearing and gas dynamical pressure radial bearing combine in the second transverse bearing 600 dynamic
On the basis of static pressure hybrid radial bearing, increase magnetic element, forms gas magnetic hybrid radial bearing, structure and the first radial axle
Hold 500 and third transverse bearing 800 be gas magnetic combined bearing when structure it is essentially identical, difference be only that the second transverse bearing
600 are not provided with magnetic element at 200 position of turbine, because of magnetic element non-refractory, correspond to Figure 10 to Figure 18, by the
Two transverse bearings 600 are set as the structural schematic diagram of the horizontal rotor system of gas magnetic hybrid radial bearing respectively such as Figure 19 to Figure 27
It is shown.
The numerous embodiments of vertical rotor system presented below.
As shown in figure 28, a kind of vertical rotor system, including shaft 100, turbine 200, compressor 300, motor 400,
One transverse bearing 500, the second transverse bearing 600 and thrust bearing 700, it is radial that the shaft 100 passes through first set gradually
Bearing 500, thrust bearing 700, motor 400, compressor 300, the second transverse bearing 600 and turbine 200, the shaft 100 exist
Rotation in first transverse bearing 500, the stator of thrust bearing 700, the stator of motor 400 and the second transverse bearing 600, institute
It states shaft 100 to be fixedly connected with the compression wheel of the turbine of the thrust disc of thrust bearing 700 and turbine 200, compressor 300, root
According to entire vertical rotor system (weight including motor 400), the quality and/or axial position of the thrust bearing 700 are adjusted,
It falls in the center of gravity of the entire rotor-support-foundation system between the first transverse bearing 500 and the second transverse bearing 600, preferably falls in and calm the anger
On machine 300.
As shown in figure 29, being only that with the difference of the vertical rotor system shown in Figure 28 will be before the thrust bearing 700
It moves, positioned at the front end of the first transverse bearing 500 (wherein the direction of motor to turbine is from front to back).
When the diameter of the thrust disc of thrust bearing 700 is smaller, when will not block gas turbine inlet, then using such as Figure 30 institute
The vertical rotor system shown, the difference with the vertical rotor system shown in Figure 28 are only that the position for moving back thrust bearing 700,
It is located between motor 400 and compressor 300, and the diameter of the thrust disc of thrust bearing 700 is smaller, combustion gas wheel will not be blocked
Machine import.
For the stability for improving entire vertical rotor system, changed in the vertical rotor system shown in Figure 28 to Figure 30
Into.For the vertical rotor system shown in Figure 28 and Figure 29, increase third transverse bearing between motor 400 and compressor 300
800；For the vertical rotor system shown in Figure 30, between thrust bearing 700 and compressor 300 or in motor 400 and push away
Third transverse bearing 800 is set between power bearing 700, referring specifically to Figure 31 to Figure 34.
Under special operation condition, can not move forward thrust bearing, then transverse bearing is arranged at entire rotor-support-foundation system both ends, make entirely to turn
Subsystem is in the spindle bodily form, so that entire rotor-support-foundation system stable structure, on this basis, since thrust bearing contains magnetic element
When, magnetic element can not be resistant to the high warm that turbine transmits, and increase a radial axle between thrust bearing 700 and turbine 200
It holds, so that thrust bearing 700 is not affected by high temperatures far from turbine 200, referring specifically to Figure 35.
As shown in figure 35, a kind of vertical rotor system, including shaft 100, turbine 200, compressor 300, motor 400,
One transverse bearing 500, the second transverse bearing 600, thrust bearing 700 and the 4th transverse bearing 801, the shaft 100 pass through according to
The first transverse bearing 500, motor 400, compressor 300, thrust bearing 700, the second transverse bearing 600, turbine 200 of secondary setting
With the 4th transverse bearing 801, the shaft 100 is in first transverse bearing 500, the stator of motor 400, thrust bearing 700
Stator, rotation in the second transverse bearing 600 and the 4th transverse bearing 801, the thrust of the shaft 100 and thrust bearing 700
The turbine of disk and turbine 200, compressor 300 compression wheel be fixedly connected.
For the stability for improving entire vertical rotor system, improved in the vertical rotor system of Figure 35, in motor
Increase third transverse bearing 800 between 400 and compressor 300, referring specifically to Figure 36.
Preferably, the first transverse bearing 500, the second transverse bearing 600 and third transverse bearing 800, the 4th transverse bearing
801 be untouchable transverse bearing.
Preferably, the second transverse bearing 600, the 4th transverse bearing 801 are externally pressurized air bearing and gas dynamic pressure diameter
The hybrid transverse bearing combined to bearing.
Preferably, the first transverse bearing 500 and third transverse bearing 800 are gas magnetic hybrid radial bearing.
Preferably, motor 400 is fluid dynamic bearing motor, and the part that motor 400 is corresponded in shaft 100 is provided with dynamic pressure
Generation trough.
Preferably, turbine 200 is provided with heat-barrier material close to the end face of the second transverse bearing 600, for example aeroge.
Preferably, compressor 300 is centrifugal compressor.
Preferably, turbine turbine is centrifugal turbine.
Preferably, the first transverse bearing 500, the second transverse bearing 600 and third transverse bearing 800, the 4th transverse bearing
801 when being untouchable transverse bearing, and when shaft 100 is inactive, shaft 100 is arranged concentrically with bearing holder (housing, cover) 530, shaft 100
After starting, so that any side in the axle center of the axis deviation bearing holder (housing, cover) 530 of shaft 100, and eccentricity epsilon is 0.3 to 0.5, with
Guarantee to be capable of forming wedge-shaped gap between bearing holder (housing, cover) 530 and shaft 100, in shaft revolution, gas is pressed into wedge-shaped gap, from
And pressure is generated to support load.EccentricityWherein, e is the axle center of shaft at a distance from the axle center of bearing holder (housing, cover), R
For the internal diameter of bearing holder (housing, cover), r is the internal diameter of shaft, and R-r is bearing clearance.
Preferably, to be that externally pressurized air bearing and gas dynamical pressure radial bearing combine in the second transverse bearing 600 dynamic
On the basis of static pressure hybrid radial bearing, increase magnetic element, forms gas magnetic hybrid radial bearing, structure and the first radial axle
Hold 500 and third transverse bearing 800 be gas magnetic combined bearing when structure it is essentially identical, difference be only that the second transverse bearing
600 are not provided with magnetic element at 200 position of turbine, because of magnetic element non-refractory, correspond to Figure 28 to Figure 36, by the
Two transverse bearings 600 are set as the structural schematic diagram of the vertical rotor system of gas magnetic hybrid radial bearing respectively such as Figure 37 to Figure 45
It is shown.
Above-mentioned horizontal rotor system and vertical rotor system are suitable for gas turbine power generation Unit erriger, preferably micro- combustion gas
Turbine generate electricity Unit erriger, wherein micro- gas turbine remove including compressor (preferably centrifugal-flow compressor), turbine (turbine 200
The preferably centrifugal turbine of turbine) outside, it further include combustion chamber (preferably toroidal combustion chamber), regenerator etc..
The course of work of micro- gas turbine power generation Unit erriger is as follows:
Below for ease of description, we will not need axis rotation and can play the bearing of lubricating action to be defined as static pressure axis
It holds, just workable bearing is defined as hydrodynamic bearing when axis turns to certain speed.Logic according to this in the following description will be electric
Magnetic bearing and hydrostatic gas-lubricated bearing are referred to as hydrostatic bearing, and hydrodynamic gas-lubricated bearing is known as hydrodynamic bearing.
S1: bearing starting: the hydrostatic bearing part in transverse bearing and thrust bearing is respectively started in control system, so that turning
Axis 100 jacks up vacantly to predetermined position, and thrust disc 701 reaches the predetermined position between the first stator 702 and the second stator 703,
With the end face gap Jun You of first stator 702 and the second stator 703；
S2: micro- gas turbine starts work, and air enters centrifugal-flow compressor by air intake duct, passes through backheat after being compressed
Device is preheated by the compressed air that the high-temperature gas that the turbine of turbine 200 is discharged exports compressor 300；Pre-add
Air after heat enters combustion chamber and fuel is mixed and burned, and the high temperature and high pressure gas after the full combustion of combustion chamber is to turbine 200
Turbine is impacted, and turbine is rotated, and turbine exhaust enters regenerator and arranged by offgas duct after blower outlet air-flow preheating
Out, it is connect due to turbine with compressor, so that turbine rotation drives compressor to rotate together and drags front end generator rotation hair
Electricity output shaft work, in the process, when the revolving speed of the shaft 100 reaches predetermined value, it is preferable that the 5%-30% of rated speed
When, control system controls the hydrostatic bearing part in transverse bearing and thrust bearing respectively and stops working, when the revolving speed of shaft 100
When crossing critical single order or second order critical speed, control system controls transverse bearing respectively and the hydrostatic bearing part of thrust bearing is opened
It is dynamic, until control system controls the hydrostatic bearing part in transverse bearing and thrust bearing respectively after steadily spending critical speed
It stops working.
S3: shutting down, and micro- gas turbine stops working, and the revolving speed of shaft 100 is gradually reduced, when 100 revolving speed of shaft crosses single order
When critical or second order critical speed, control system controls the hydrostatic bearing part starting of transverse bearing and thrust bearing respectively, directly
To after steadily spending critical speed, control system controls the hydrostatic bearing part in transverse bearing and thrust bearing respectively and stops work
Make；When the revolving speed of the shaft 100 is down to predetermined value, it is preferable that when the 5%-30% of rated speed, control system controls diameter respectively
To the starting of the hydrostatic bearing part of bearing and thrust bearing after revolving speed is reduced to 0, the control system controls radial axle respectively
It holds and stops working with the hydrostatic bearing part in thrust bearing.
Preferably, in step S1, the air intake duct is made of the shell and micro- gas turbine shell of generator, the air
Cooling effect is played to generator during entering centrifugal-flow compressor by air intake duct.
Preferably, the compressor 300 includes movable vane and stator blade, and further preferably, the stator blade is diffuser, the step
In rapid S2: the process of " air enters centrifugal-flow compressor by air intake duct, is compressed " are as follows: air enters centrifugal-flow compressor movable vane
Diffuser (stationary parts) continuation entered after being compressed circumferentially is compressed.
Preferably, the turbine of the turbine 200 includes stator blade and movable vane, and further preferably, the stator blade is nozzle, described
" high temperature and high pressure gas after the combustion chamber full combustion impacts the turbine of turbine 200, revolves turbine in step S2
Turn " process are as follows: high temperature and high pressure gas after the combustion chamber full combustion is (quiet by the nozzle of combustor exit circumferentially
Stop part) carry out expansion acceleration after, (i.e. combustion gas continues expansion and to turbine work done) is impacted to turbine rotor blade, revolves turbine
Turn.
More than, only specific embodiment of the present utility model, but protection scope of the utility model is not limited thereto,
Anyone skilled in the art within the technical scope disclosed by the utility model, can readily occur in variation or replace
It changes, should be covered within the scope of the utility model.Therefore, the protection scope of the utility model should be with claim
Subject to protection scope.
Claims (13)
1. a kind of bearing damp device, which is characterized in that the bearing damp device is for being installed in non-contact type bearing, the axis
It holds damper to be made of shape-memory material, the bearing damp device can pass through plastic deformation adjustment stationary parts and rotating part
Bearing clearance between part.
2. bearing damp device according to claim 1, which is characterized in that the bearing damp device includes at least two adjustment
Unit；
The bearing damp device is the integral device that formation is continuously arranged at least two adjustment unit；Alternatively,
The bearing damp device includes at least two adjustment members being independently arranged, and the adjustment member includes described at least one
Adjustment unit.
3. bearing damp device according to claim 2, which is characterized in that the adjustment unit is half shell structure, including
Lug boss and support portion, the lug boss and the support portion are integrally formed.
4. a kind of transverse bearing, which is characterized in that the transverse bearing includes:
Bearing body；
The bearing inner race being sheathed in the bearing body, the bearing inner race and being sheathed between the shaft in bearing inner race have
There is bearing clearance；
And it is set to bearing described in any one of claims 1 to 3 between the bearing inner race and the bearing body
Damper, the bearing damp device can be plastically deformed under the action of the bearing inner race, to adjust between the bearing
Gap.
5. transverse bearing according to claim 4, which is characterized in that the adjustment unit of the bearing damp device is half shell
Structure；
The lug boss of the bearing damp device is towards the bearing inner race, the support portion of the bearing damp device and the bearing sheet
The aperture surface of body is affixed setting；
The lug boss can be plastically deformed under the action of the bearing inner race, to adjust the bearing clearance.
6. transverse bearing according to claim 4, which is characterized in that the bearing damp device is independently set including at least two
The adjustment member set；
The adjustment member is circumferentially uniformly distributed along the aperture surface of the bearing body；And/or
The adjustment member is axially uniformly distributed along the aperture surface of the bearing body.
7. transverse bearing according to claim 4, which is characterized in that the aperture surface of the bearing inner race or the shaft court
Dynamic pressure generation trough is provided on the periphery of the bearing inner race；
And/or
The transverse bearing is provided with the static pressure air inlet restriction hole for being connected to the bearing clearance and external gas source, the static pressure air inlet
Throttle orifice is for external gas source to be delivered in the bearing clearance；
And/or
Multiple magnetic parts are provided on the bearing body, the shaft can be in the magneticaction of the multiple magnetic part
Under moving in the radial direction in the shaft.
8. a kind of thrust bearing, for being installed on shaft, which is characterized in that the thrust bearing includes:
Thrust disc, the thrust disc are connected in the shaft；
And it is arranged in the first stator and the second stator in the shaft, first stator and second stator difference
It is set to the opposite sides of the thrust disc；
In first stator and second stator, each stator includes appointing in stator body, pressing plate and claims 1 to 3
Bearing damp device described in one, the bearing damp device are set between the stator body and the pressing plate, the pressing plate
It is set to the side close to the thrust disc of the stator body, between bearing between the pressing plate and the thrust disc
Gap；
Wherein, the bearing damp device can be plastically deformed under the action of the pressing plate, to adjust the bearing clearance.
9. thrust bearing according to claim 8, which is characterized in that the adjustment unit of the bearing damp device is half shell
Structure；
The lug boss of the bearing damp device is towards the pressing plate, the support portion of the bearing damp device and the stator body phase
It is sticked and sets；
The lug boss can be plastically deformed under the action of the pressing plate, to adjust the bearing clearance.
10. thrust bearing according to claim 8, which is characterized in that the bearing damp device includes at least two independent
The adjustment member of setting；
The adjustment member is circumferentially uniformly distributed along the end face of the stator body；And/or
End face radial equipartition of the adjustment member along the stator body.
11. thrust bearing according to claim 8, which is characterized in that the end face towards the thrust disc of the pressing plate
Or the thrust disc towards being provided with dynamic pressure generation trough on the end face of the pressing plate；
And/or
In first stator and second stator, the connection bearing clearance and external gas source are additionally provided on each stator
Static pressure air inlet restriction hole, static pressure air inlet restriction hole is for external gas source to be delivered in the bearing clearance；
And/or
It is provided with the first magnetic part on the thrust disc, multiple second magnetic parts, institute are additionally provided on the stator body
Stating thrust disc can be under the magneticaction between first magnetic part and the multiple second magnetic part at described turn
It is moved on the axial direction of axis.
12. a kind of rotor-support-foundation system, which is characterized in that including shaft, thrust bearing and at least two transverse bearings, the thrust axis
It holds and is mounted in the shaft at least two transverse bearing, the thrust bearing and at least two transverse bearing
It is non-contact type bearing；
Wherein, at least one transverse bearing at least two transverse bearing is described in any one of claim 4 to 7
Transverse bearing；And/or the thrust bearing is thrust bearing described in any one of claim 8 to 11.
13. rotor-support-foundation system according to claim 12, which is characterized in that
The axis body of the shaft is structure as a whole, and the shaft is horizontally disposed or vertically arranged；
Motor, compressor and turbine are also disposed in the shaft；
Wherein, the thrust bearing is set on the predeterminated position of the side of the close compressor of the turbine, described pre-
If position is two radial directions that the center of gravity of the rotor-support-foundation system can be made to be located at lie farthest away at least two transverse bearing
Position between bearing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821612816.XU CN208858777U (en) | 2018-09-30 | 2018-09-30 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201821612816.XU CN208858777U (en) | 2018-09-30 | 2018-09-30 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
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| Publication Number | Publication Date |
|---|---|
| CN208858777U true CN208858777U (en) | 2019-05-14 |
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ID=66420060
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201821612816.XU Active CN208858777U (en) | 2018-09-30 | 2018-09-30 | A kind of bearing damp device, transverse bearing, thrust bearing and rotor-support-foundation system |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110243601A (en) * | 2019-07-08 | 2019-09-17 | 淮海工学院 | Combination thrust and transverse bearing device and its detection method under a kind of operating condition suitable for ultrahigh speed |
| CN111288082A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Control system of single-degree-of-freedom magnetic-liquid double-suspension bearing |
| CN111288081A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control system |
| CN111350757A (en) * | 2019-12-11 | 2020-06-30 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control method |
| WO2021143415A1 (en) * | 2020-01-19 | 2021-07-22 | 至玥腾风科技集团有限公司 | Air bearing comprising adaptive damper |
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2018
- 2018-09-30 CN CN201821612816.XU patent/CN208858777U/en active Active
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110243601A (en) * | 2019-07-08 | 2019-09-17 | 淮海工学院 | Combination thrust and transverse bearing device and its detection method under a kind of operating condition suitable for ultrahigh speed |
| CN110243601B (en) * | 2019-07-08 | 2020-10-09 | 淮海工学院 | Combined thrust and radial bearing device suitable for ultra-high-speed working condition and detection method thereof |
| CN111288082A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Control system of single-degree-of-freedom magnetic-liquid double-suspension bearing |
| CN111288081A (en) * | 2019-12-11 | 2020-06-16 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control system |
| CN111350757A (en) * | 2019-12-11 | 2020-06-30 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control method |
| CN111350757B (en) * | 2019-12-11 | 2021-12-21 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control method |
| CN111288081B (en) * | 2019-12-11 | 2022-03-11 | 燕山大学 | Single-degree-of-freedom magnetic-liquid double-suspension bearing control system |
| WO2021143415A1 (en) * | 2020-01-19 | 2021-07-22 | 至玥腾风科技集团有限公司 | Air bearing comprising adaptive damper |
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