CN101326377B - Magnetic bearing device - Google Patents
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- CN101326377B CN101326377B CN2006800459209A CN200680045920A CN101326377B CN 101326377 B CN101326377 B CN 101326377B CN 2006800459209 A CN2006800459209 A CN 2006800459209A CN 200680045920 A CN200680045920 A CN 200680045920A CN 101326377 B CN101326377 B CN 101326377B
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Abstract
A magnetic bearing device is provided. The magnetic bearing device is stably controllable with a simplified-structure controller, and a roller bearing and a magnetic bearing are used in combination for the magnetic bearing device. The roller bearing and the magnetic bearing are used in combination in the magnetic bearing device, wherein the roller bearing supports a radial load while the magnetic bearing supports either the axial load or precompression or both. An electromagnet (17) is provided at a spindle housing (14) opposite in non-contact to a flange-like thrust plate (13a) which is fixed perpendicularly and coaxially at a main spindle (13) and which is made of ferromagnetic materials. A sensor (18) is provided to detect an axial direction force to act on the roller bearing and a controller (19) is further provided to control electromagnet (17) in response to an output of the sensor (18). The bearing device has the relationship that a resultant spring-stiffness value formed by the roller bearing and its supporting system is larger than a minus stiffness value of the electromagnet.
Description
Technical field
The present invention relates to a kind of magnetic bearing device, and it is with rolling bearing and magnetic bearing, by magnetic bearing, bears any one or both in axial load and the bearing prepressing force, the present invention relates to such as, the magnetic bearing device that the turbine assembly in the air cycle refrigerating/cooling system etc. is adopted.
Background technique
In air cycle refrigerating/cooling system, because refrigeration agent adopts air, so compare with the occasion that adopts fluorine carbon refrigerant, ammonia etc., the energy efficiency deficiency still, is good aspect environmental protection.In addition,, can directly be blown in the facility of cooling air, have because of the omission of storehouse internal fan, windshield heater etc., reduce the possibility of overall cost as freezer etc., in such purposes, propose that air cycle refrigerating/cooling system is arranged (such as, patent documentation 1).
In addition, people know that in-30 ℃～-60 ℃ deep cooling zone, air cooled theoretical efficiency is more than or equal to fluorine carbon refrigerant, ammonia.But people also mention, and obtain the peripheral device that includes optimal design of above-mentioned air cooled theoretical efficiency, and it begins to set up.Peripheral device is compressor, expansion turbine etc.
As compressor, expansion turbine, adopt compressor blade and the turbine assembly (patent documentation 1) of expansion turbine blade installation on common main shaft.
In addition, turbine assembly as treatment process gas, people propose to have magnetic bearing formula turbine assembly, wherein, end at main shaft is installed turbine bucket, at its other end compressor blade is installed, the magnetic bearing formula turbine assembly (patent documentation 2) that supports above-mentioned main shaft by axle journal and thrust-bearing by current of electromagnet control.
Also have, though people propose that gas-turbine engine is arranged,, for fear of acting on the shortening that thrust load on the rolling bearing that main shaft supporting uses causes bearing life, people propose to reduce to act on the thrust load (patent documentation 3) on the rolling bearing by the thrust magnetic bearing.
Patent documentation 1: No. 2623202 document of Japan's special permission
Patent documentation 2: Japanese kokai publication hei 7-91760 document
Patent documentation 3: Japanese kokai publication hei 8-261237 document
As described above, as air cycle refrigerating/cooling system, in order to obtain to necessarily require compressor, the expansion turbine of optimal design at the high efficiency air cooled theoretical efficiency in deep cooling zone.
As compressor, expansion turbine, as described above, adopt compressor blade and the turbine assembly of expansion turbine blade installation on common main shaft.In this turbine assembly, by the power that expansion turbine produced, but the Driven Compressor blade thus, improves the efficient of air circulation refrigerating machine.
But, in order to obtain practical efficient, the gap that must keep each blade and shell minutely.The variation in this gap constitutes the obstruction of stable high speed rotating, causes the reduction of efficient.
In addition,, on main shaft, act on thrust, applied thrust load on the bearing of supporting spindle by acting on the air on compressor blade, the expansion turbine blade.The rotational speed of the main shaft of the turbine assembly in the air cycle refrigerating/cooling system is per 1 minute 8～100,000 commentaries on classics, compares with the bearing of general applications, and be very high speed.Thus, above-mentioned such thrust load reduces the durability of the bearing of supporting spindle, and the life-span reduces, and the freezing cooling of air circulation is reduced with the reliability of turbine assembly.Do not solve the problem of the long durability of such bearing, the freezing cooling of air circulation is difficult to practicability with turbine assembly.But disclosed technology is not that reduction at the long durability of the bearing of the load of the thrust load under the relative high speed rotating of bearing solves in the above-mentioned patent documentation 1.
As the magnetic bearing formula turbomachine compressor of patent documentation 2, by the shaft bearing and the thrust-bearing supporting spindle that are formed by magnetic bearing, shaft bearing does not have axial limitation function.Thus, if having the unstable reason etc. of the control of thrust-bearing, then be difficult to keep the micro-gap between above-mentioned blade and the windshield heater and carry out stable high speed rotating.In the occasion of magnetic bearing, also has the problem of the contact of power supply when stopping.
If the supporting of main shaft and with rolling bearing and magnetic bearing, rolling bearing bears radial load, and magnetic bearing bears any one or both in axial load and the bearing prepressing force, then leads axial restriction, the problem of the contact when in addition, the power supply that does not also produce the occasion of magnetic bearing stops.Occasion in this scheme, according to the mode that does not contact with the flange shape thrust plate that forms by the strong magnetism body of the vertical and coaxial setting of main shaft and face, the electromagnet of magnetic bearing is set, corresponding to the output of the sensor that detects axial power, by controller control electromagnet.
If by rolling bearing, the main shaft of supporting blade, then by the limitation function of the axial position that rolling bearing had, the restriction main spindle's can keep the micro-gap of each blade and shell certain.In the occasion of the rolling bearing of the limitation function with such axial position, the reduction of the long durability of the above-mentioned thrust of the bearing of high speed rotating becomes problem, still, because by electromagnet supporting thrust, so can guarantee the long durability of rolling bearing.
But, and magnetic bearing device with such rolling bearing and magnetic bearing in, the occasion that excessive axial load is arranged in effect, the negative rigidity of electromagnet is (along the directive effect that is subjected to displacement, displacement is big more, and its power is also big more) increase the rigidity of the synthetic spring that the negative rigidity of above-mentioned electromagnet forms greater than the supporting system by rolling bearing and rolling bearing, at this moment, the control system instability of magnetic bearing.For fear of this state, has additive phase compensating circuit in controller in advance, the problem of one of reason of formation controller complexity.
Summary of the invention
The object of the present invention is to provide a kind of and with the magnetic bearing device of rolling bearing and magnetic bearing, wherein, can carry out stable control, the structure of controller also can be simplified.
The magnetic bearing device of the 1st scheme of the present invention is also used rolling bearing and magnetic bearing, rolling bearing supporting radial load, magnetic bearing bears any one or both in axial load and the bearing prepressing force, electromagnet is according to vertical with main shaft and mode that the flange shape thrust plate that is formed by the strong magnetism body that be provided with is coaxially faced non-contactly is installed on the main shaft shell, have corresponding to the output of detection effect in the sensor of axial power, the controller of control electromagnet has the relation of the values of stiffness of the synthetic spring that the supporting system by rolling bearing and rolling bearing forms greater than the values of stiffness of bearing of electromagnet.
In the magnetic bearing device of the 1st scheme, because also with rolling bearing and magnetic bearing, rolling bearing bears radial load, magnetic bearing bears any one or both in axial load and the bearing prepressing force, so carry out the good supporting of axial precision, in addition, can guarantee the long durability of rolling bearing, avoid the damage when only the power supply of the occasion of the supporting of magnetic bearing stops.
In addition, owing to form the relation of the values of stiffness of the synthetic spring that the supporting system by rolling bearing and rolling bearing forms greater than the negative values of stiffness of electromagnet, so can prevent from controlling frequency band, the phase delay of mechanical system is 180 ° situation.Thus, controlling object is stable, and the circuit structure of controller is the simple structure of ratio or proportional integral etc., even like this, still can carry out stable control.
In the magnetic bearing device of the 1st scheme, also the values of stiffness of the synthetic spring that can form at the supporting system by rolling bearing and rolling bearing is that Kbrg, maximum load are that Fmax, electromagnet gap are that d, proportionality constant are the occasion of k, has the electromagnet gap of satisfying the condition expression of being represented by following formula: d＞k * Fmax/Kbrg.It constitutes the magnetic bearing device of the 2nd scheme.
In the magnetic bearing device of the 2nd scheme, owing to the electromagnet gap is set according to the mode that satisfies above-mentioned condition expression, even so in the high speed rotating zone, under the condition of the bearing prepressing force of best light load, by enlarging the electromagnet gap, can keep the relation of the values of stiffness of the synthetic spring that the supporting system by rolling bearing and rolling bearing forms greater than the values of stiffness of bearing of electromagnet.Consequently, can prevent in the control frequency band that the situation that the phase delay of mechanical system is 180 ° thus, even under the situation of maximum load effect, still can make controlling object stable, but passing ratio or proportional integral, the circuit structure of simplification controller.
In addition, in the magnetic bearing device of the 1st scheme, also can permanent magnet be set in the inside of the yoke of above-mentioned electromagnet.It constitutes the magnetic bearing device of the 3rd scheme.
Magnetic bearing device according to the 3rd scheme, under the condition of the bearing prepressing force of the best light load in high speed rotating zone, for the magnitude relationship between the negative values of stiffness of the values of stiffness that keeps above-mentioned synthetic spring and electromagnet, must reduce the negative rigidity of electromagnet, still, as described above, yoke inside at electromagnet is provided with permanent magnet, thus, enlarges the electromagnet gap, like this, can reduce the negative rigidity of electromagnet.
In addition, even under the situation of the maximum axial load of effect, above-mentioned permanent magnet is arranged at the inside of the yoke of electromagnet, and the power consumption of electromagnet reduces, and can reduce the heating of electromagnet.
Also have, in the magnetic bearing device of the 1st scheme, also above-mentioned permanent magnet only can be arranged at the inside of yoke of electromagnet of a side of above-mentioned thrust plate, in the light load zone of axial load, and use with permanent magnet be arranged at yoke inside electromagnet and this permanent magnet is arranged at yoke inside electromagnet in the face of and the electromagnet that does not comprise permanent magnet that is provided with.It is the magnetic bearing device of the 4th scheme.
According to the magnetic bearing device of the 4th scheme, because in the light load zone of axial load, and use the electromagnet that permanent magnet is arranged at yoke inside; With above-mentioned electromagnet in the face of and the electromagnet that does not comprise permanent magnet that is provided with, so the power consumption of the interior electromagnet of the actuating range that can farthest reduce axial load and acted on.That is, two sides of the electromagnet of being faced, the occasion of permanent magnet is set, in the light load zone of axial load, reduces the attraction force of permanent magnet, the power consumption of electromagnet increases, and heating increases, and still, can eliminate this situation by the 4th scheme.
In the magnetic bearing device of the 4th scheme, the electromagnet that also above-mentioned permanent magnet can be arranged at yoke inside is arranged on a side of bearing excessive axial load, and the electromagnet that does not comprise above-mentioned permanent magnet is with the above-mentioned thrust plate of clamping, be provided with in the face of the ground mode with the electromagnet of the inside that above-mentioned permanent magnet is arranged at yoke.It constitutes the magnetic bearing device of the 5th scheme.
The magnetic bearing device of the 1st scheme also can be following form, wherein, compressor side blade and turbo machine lateral lobe sheet be embedded in the common main shaft of above-mentioned thrust plate on, by the power that produces by turbo machine lateral lobe sheet, in the compression-expansion turbine system of Driven Compressor lateral lobe sheet, be applicable to the supporting of above-mentioned main shaft.It constitutes the magnetic bearing device of the 6th scheme.
In the occasion of the 6th scheme, effectively performance can be carried out the stable control of magnetic bearing device of the present invention, the also reducible advantage of the structure of controller, and the blade end gap that is fit to that keeps each blade obtains the stable high speed rotating of main shaft.In addition, realize the raising of the long durability of bearing.
The magnetic bearing device of the 1st scheme also can be following form, wherein, the compression-expansion turbine system that is suitable for above-mentioned magnetic bearing device is applicable to relative inflow air, carries out the compression, the air cycle refrigerating/cooling system of heat insulation expansion that other the expansion turbine of cooling, above-mentioned turbine assembly of heat exchanger produces of compressor of cooling, the turbine assembly of compression, the heat exchanger of precompression mechanism successively.It constitutes the magnetic bearing device of the 7th scheme.
Be applicable to the occasion of such air cycle refrigerating/cooling system at the compression-expansion turbine system that is suitable for above-mentioned magnetic bearing device, in the compression-expansion turbine system, the blade tip gap that is fit to that keeps each blade, obtain the stable high speed rotating of main shaft, and the long durability of bearing improves, thus, as the integral body of compression-expansion turbine system, and then improve as the whole reliability of air cycle refrigerating/cooling system.In addition, stable high speed rotating, long durability, the reliability of the main shaft bearing of the compression-expansion turbine system of the weak link of formation air cycle refrigerating/cooling system improves, and thus, air cycle refrigerating/cooling system can drop into practicality.
Description of drawings
Explanation according to reference to the accompanying drawings following preferred embodiment can be expressly understood the present invention more.But embodiment and accompanying drawing are used for simple diagram and explanation, should not determine scope of the present invention.Scope of the present invention is determined by the scope of accompanying Claim.In the accompanying drawings, the identical parts label in a plurality of accompanying drawings is represented same part.
Fig. 1 is the sectional view of turbine assembly that is assembled with the magnetic bearing device of the 1st example of the present invention;
Fig. 2 is the skeleton diagram of an example of the controller that turbine assembly adopted of presentation graphs 1;
Fig. 3 is the sectional view of turbine assembly that is assembled with the magnetic bearing device of the 2nd example of the present invention;
Fig. 4 is the sectional view of turbine assembly that is assembled with the magnetic bearing device of the 3rd example of the present invention;
Fig. 5 (A) is the amplification view of another example of the electromagnet in the magnetic bearing device of expression the 3rd example, and Fig. 5 (B) goes back the amplification view of an example for expression;
Fig. 6 is the electromagnet at built-in permanent magnet, with the electromagnet of the monomer of built-in permanent magnet not, and the plotted curve of the relation between expression suction and the power consumption;
Fig. 7 is the sectional view of turbine assembly that is assembled with the magnetic bearing device of the 4th example of the present invention;
Fig. 8 for along the VI-VI line among Fig. 7 to looking sectional view;
Fig. 9 is the sectional view of turbine assembly that is assembled with the magnetic bearing device of the 5th example of the present invention;
Figure 10 is illustrated in and with the occasion of two electromagnet of magnetic bearing device, and axial load is the bar chart of power consumption of the electromagnet part of light load, shoulder load, busy hour;
Figure 11 is the occasion that two electromagnet being illustrated in magnetic bearing device adopt the electromagnet of built-in permanent magnet, and axial load is the bar chart of power consumption of the electromagnet part of light load, shoulder load, busy hour;
Figure 12 is that two electromagnet that are illustrated in magnetic bearing device adopt the not occasion of the electromagnet of built-in permanent magnet, and axial load is the bar chart of the electromagnet power consumption partly of light load, shoulder load, busy hour;
Figure 13 is the system diagram of the air cycle refrigerating/cooling system of the turbine assembly that adopts the magnetic bearing device be assembled with the 1st～the 5th example.
Embodiment
In conjunction with Fig. 1 and Fig. 2, the 1st example of the present invention is described.Fig. 1 represents to be assembled with the sectional view of the turbine assembly 5 of magnetic bearing device of the present invention.This turbine assembly 5 constitutes the compression-expansion turbine system, and it comprises compressor 6 and expansion turbine 7, and the compressor blade 6a of this compressor 6 and the turbine bucket 7a of expansion turbine 7 are installed on the two ends of main shaft 13 respectively.In addition, by the power that is produced by turbine bucket 7a, Driven Compressor blade 6a is not provided with other driving source.
Magnetic bearing device in this turbine assembly 5 relatively radially by a plurality of bearing 15,16 supporting spindles 13, by constituting the electromagnet 17 of magnetic bearing, bears the thrust that acts on the main shaft 13.This turbine assembly 5 comprises sensor 18, and this sensor 18 detects by the air in compressor 6 and the expansion turbine 7, acts on the thrust on the main shaft 13; Controller 19, this controller 19 are controlled the supporting force of electromagnet 17 corresponding to the output of this sensor 18.Electromagnet 17 is according in the centre of main shaft 13, and being arranged to admit with mode that the two sides of the flange shape thrust plate 13a that is formed by the strong magnetism body of main shaft 13 vertical and coaxial settings is faced non-contactly has on the main shaft shell 14 of main shaft.
The bearing 15,16 of supporting spindle 13 is a rolling bearing, has the limitation function of axial position, such as, adopt deep trouth ball bearing, angular contact ball bearing.In the occasion of deep trouth ball bearing, have two-way thrust and bear function, have the effect that the axial position of Internal and external cycle is turned back to the neutral position.These 2 bearings 15,16 be arranged at respectively compressor blade 6a in the main shaft shell 14 and turbine bucket 7a near.
Each blade 6a in the bearing 15,16 of the both sides in the main shaft shell 14, the part of 7a side form according to the diameter of aperture surface near main shaft 13, form non-contact Sealing 21,22 on this aperture surface.In this example, non-contact Sealing 21,22 constitutes labyrinth, wherein, on the aperture surface of main shaft shell 14, is formed with a plurality of circumferential grooves vertically side by side, still, also can be other non-contact Sealing.
The sensor 18 is arranged near the Stationary side of the bearing 16 of turbine bucket 7a side, that is, and and main shaft shell 14 sides.The outer ring 16b of bearing 16 that is provided with this sensor 18 nearby is embedded in the inside of bearing shell 23 at stationary state.Bearing shell 23 at one end has the inward flange 23a that engages with the breadth of the outer ring 16b of bearing 16 in the form of a ring, and is chimeric with the aperture surface 24 that is arranged on the main shaft shell 14 according to axially displaceable mode.Inward flange 23a is arranged at axial middle side.
Owing to pass through pressing force, even the sensor 18 that detects thrust moves relative to the axial any direction of main shaft 13, still can detect,, act on the above value of average thrust on the main shaft 13 so the precompressed of sensor loaded spring 25 is the common operating condition at turbine assembly 5.
The bearing 15 that sensor 18 non-is provided with side is according to main shaft shell 14 relatively, and the mode of Yi Donging is provided with vertically, and flexibly supports by bearing prepressing force spring 26.In this example, the outer ring 15b of bearing 15 is embedded in according to axially displaceable mode on the aperture surface of main shaft shell 14, and bearing prepressing force spring 26 is situated between and is located between outer ring 15b and the main shaft shell 14.Bearing prepressing force spring 26 applies precompressed according to making outer ring 15b biasing with mode that the step surface of the main shaft that breadth engaged 13 of inner ring 15a is faced to bearing 15.Bearing prepressing force spring 26 constitutes by being arranged at around the helical spring at a plurality of positions of the circumferencial direction of main shaft 13 etc., is received in respectively in the admittance recess that is arranged on the main shaft shell 14.The spring constant of bearing prepressing force spring 26 is less than sensor loaded spring 25.
The mechanical model of the magnetic bearing device in the above-mentioned turbine assembly 5 can constitute by simple spring system.That is, this spring system is following scheme, and wherein, the synthetic spring that is made of the supporting system (sensor loaded spring 25, bearing prepressing force spring 26, bearing shell 23 etc.) of bearing 15,16 and these bearings and the spring of electromagnet 17 are arranged side by side.In this spring system, the synthetic spring that is made of the supporting system of bearing 15,16 and these bearings has proportional along direction opposite with direction of displacement and displacement amount and rigidity that act on, relative this situation, the spring of electromagnet 17 have the negative rigidity along direction of displacement and the proportional effect of displacement amount.
Thus, the magnitude relationship in the rigidity of the spring of above-mentioned synthetic spring and electromagnet is:
The negative values of stiffness of the rigidity＜electromagnet of synthetic spring ... (1)
Occasion, 180 ° of the phase delays of mechanical system form unsettled system, thus, in the controller 19 of control electromagnet 17, additive phase compensating circuit in advance, the complex structure of controller 19.
So in the magnetic bearing device of this example, the magnitude relationship of the rigidity of the spring of the rigidity of above-mentioned synthetic spring and electromagnet 17 is:
The negative values of stiffness of the rigidity＞electromagnet of synthetic spring ... (2)
As, the magnitude relationship of the rigidity of the spring by setting above-mentioned synthetic spring and electromagnet can prevent in control frequency band, the situation that the phase delay of mechanical system is 180 °.Thus, can make the controlling object of controller 19 stable, but image pattern 2 is such, proportionally, or proportional integral constitutes the circuit structure of controller 19 simply.
In controller 19 by the Fig. 2 shown in the skeleton diagram, by sensor output arithmetic circuit 27, detection output P1, P2 to each sensor 18 carry out signed magnitude arithmetic(al), by comparator 28, this operation result is compared with the desired value of benchmark setting device 29, deviation is carried out computing, also by PI compensating circuit (or P compensating circuit) 30, to the deviation of computing, carry out corresponding and proportional integral (or ratio) that suitably set is handled with turbine assembly 5, thus, the control signal of electromagnet 17 is carried out computing.The output of PI compensating circuit (or P compensating circuit) 30 is via diode 31,32, be input to drive each to electromagnet 17
1, 17
2 Power circuit 33,34 in.Electromagnet 17
1, 17
2Be a pair of electromagnet of facing with thrust plate 13a shown in Figure 1 17, only act on attractively, thus, determine senses of current by diode 31,32 in advance, drive 2 electromagnet 17 selectively
1, 17
2
Like this, in the magnetic bearing device of the 1st example that is applicable to turbine assembly 5, owing to as (2) formula, set the magnitude relationship of the rigidity of bearing of the spring of above-mentioned synthetic spring and electromagnet 17, so can form the stable scheme of controlling object that makes controller 19, the circuit arrangement that can make controller 19 is the simple proposal of ratio or proportional integral.
Below by Fig. 3 and Fig. 2 of in the explanation of the 1st example, providing, the 2nd example of the present invention is described.Fig. 3 represents to be assembled with the sectional view of turbine assembly 5 of the magnetic bearing device of this example.In this example, the aspect common with the 1st example adopts same label in the drawings, and it illustrates omission.
The structure of turbine assembly of magnetic bearing device that is assembled with the 2nd example is identical with the 1st example, and different aspects is also to set the electromagnet gap as illustrated below.
So also the magnetic bearing device with the 1st example is identical for the magnetic bearing device of this 2nd example, the magnitude relationship of the rigidity of the spring of synthetic spring and electromagnet satisfies above-mentioned (2) formula.
On the other hand, in the scheme of above-mentioned magnetic bearing device, in high speed rotating (80,000～100,000 rpm) zone, preferably the axial precompressed of the bearing 15,16 that is provided by sensor loaded spring 25 and bearing prepressing force spring 26 is light load, if but axially precompressed is light load, then the axial stiffness of bearing 15,16 reduces, and the rigidity of the synthetic spring that is formed by the supporting system of bearing 15,16 and bearing 15,16 also diminishes.Consequently, in the occasion of the excessive axial load of effect,, must reduce the negative rigidity of electromagnet 17 for the magnitude relationship of above-mentioned (2) formula between the negative rigidity of the spring of the values of stiffness that keeps synthetic spring and electromagnet 17.In addition, in order to reduce the negative rigidity of electromagnet 17, must enlarge the electromagnet gap.
Values of stiffness at above-mentioned synthetic spring is Kbrg, and the negative values of stiffness of electromagnet 17 is Kns, and maximum load is Fmax, and the electromagnet gap is d, and when proportionality constant was k, the negative values of stiffness Kns of electromagnet 17 represented by following relation (3):
kns＝k×Fmax/d ......(3)
The magnitude relationship of above-mentioned (2) formula is represented by following relation:
Kbrg＞Kns ......(4)
So, in the magnetic bearing device of the 2nd example, in order to keep the magnitude relationship of above-mentioned (2) formula, the relation according to (3) and (4) formula, satisfy following condition expression according to the electromagnet gap d:
d＞k×Fmax/Kbrg ......(5)
Mode set.
Like this, set the electromagnet gap d according to the mode that satisfies the condition expression of representing by above-mentioned (5) formula, thus, even be under the condition of bearing prepressing force of the light load that the high speed rotating zone is best, still can keep the magnitude relationship of above-mentioned (2) formula by enlarging the electromagnet gap d.Consequently, owing to can prevent at the control frequency band, the situation that the phase delay of mechanical system is 180 °, thus, even have in effect under the situation of maximum load, still can make the controlling object of controller 19 stable, can provide Fig. 2 as the explanation of the 1st example, passing ratio or proportional integral constitute the circuit structure of controller 19 simply.In addition, because the circuit structure of this controller 19 is also identical with the 1st example, so its explanation is omitted.
Like this, in the magnetic bearing device of the 2nd example that is applicable to turbine assembly 5, set the magnitude relationship of rigidity of the spring of above-mentioned synthetic spring and electromagnet according to the mode of the above-mentioned formula (2) that in the explanation of the 1st example, provides, in addition, mode according to the condition expression that satisfies (5) formula is set the electromagnet gap d, thus, even have in effect under the situation of maximum load, can form the stable scheme of controlling object that makes controller 19, the circuit structure that can form controller 19 is the simple proposal of ratio or proportional integral.
Below in conjunction with Fig. 4～Fig. 6,, the 3rd example of the present invention is described with the Fig. 2 that in the explanation of the 1st example, provides.Fig. 4 represents to be assembled with the sectional view of turbine assembly 5 of the magnetic bearing device of this example.In this example, the aspect common with the 1st example adopts same label in the drawings, and it illustrates omission.
Be assembled with the turbine assembly of magnetic bearing device of the 3rd example and the difference of the 1st example and be that electromagnet is built-in with permanent magnet as explanation below.
So the magnetic bearing device of the 3rd example also magnetic bearing device with the 1st example is identical, the magnitude relationship of the rigidity of synthetic spring and electromagnet satisfies above-mentioned (2) formula.
On the other hand, as in the 2nd example, illustrating, in the scheme of above-mentioned magnetic bearing device, in high speed rotating (80,000～100,000 rpm) zone, the bearing prepressing force of the bearing 15,16 that is provided by bearing prepressing force spring 25, sensor loaded spring 26 is preferably light load, still, if axially precompressed is light load, then the axial stiffness of bearing 15,16 reduces, and the rigidity of the synthetic spring that is formed by the supporting system of bearing 15,16 and bearing 15,16 also reduces.Consequently, the occasion of excessive axial load is arranged,, must reduce the negative rigidity of electromagnet 17 for the magnitude relationship of above-mentioned (2) formula between the negative values of stiffness of the spring of the values of stiffness that keeps synthetic spring and electromagnet 17 in effect.In addition, in order to reduce the negative rigidity of electromagnet 17, must enlarge the electromagnet gap.
So, in the magnetic bearing device of the 3rd example, in order to keep the magnitude relationship of above-mentioned (2) formula, in two electromagnet 17 of clamping thrust plate 13a, the inside of the yoke 17a of the electromagnet 17 of a side that is provided with sensor 18 adjacency is provided with permanent magnet 20, thus, enlarge this electromagnet gap.Also the electromagnet 17 of permanent magnet 20 with both sides can be provided with, still best, as this example, only form in the electromagnet 17 of a side scheme of built-in permanent magnet 20.In Fig. 4, in order to reduce the magnetic leakage flux of permanent magnet 20, inside at the yoke 17a of the outside diameter of the coil 17b of electromagnet 17, annular permanent 20 with the concentric one of main shaft 13 is set, but, even such at image pattern 5 (B), the inside of the yoke 17a of the internal side diameter of the coil 17b of electromagnet 17 is provided with under the situation of permanent magnet 20, still can reduce the magnetic leakage flux of permanent magnet 20.In addition, in Fig. 4, in approaching pole surface from electromagnet 17, the position of the axial end of the coil 17b that retreats to the inside is provided with permanent magnet 20, still, also but image pattern 5 (A) is such, and the position at the axial intermediate portion of coil 17a is provided with permanent magnet 20.
Fig. 6 presents the plotted curve of characteristic of the attraction force of relative power consumption for the electromagnet 17 of the built-in permanent magnet 20 of expression, the electromagnet 17 of the monomer of not built-in permanent magnet 20.As according to this figure and clear, in the electromagnet 17 that is built-in with permanent magnet 20 (plotted curve A), effect has the attraction force of permanent magnet 20, and thus, the power consumption when effect has maximum load can be less than the electromagnet 17 (plotted curve B) of monomer.In addition, in plotted curve A, the part of being represented by symbol I represents that permanent magnet 20 is arranged at the characteristic of occasion of the pole surface of electromagnet 17, and the part of being represented by symbol H presents the characteristic of occasion that permanent magnet 20 is arranged at the inside of yoke 17a.Know thus, be arranged in the scheme of pole surface at permanent magnet 20, the magnetic leakage flux of permanent magnet 20 increases, magnetic field by electromagnet coil 17b, the attraction force of permanent magnet 20 is that zero situation is difficult to produce, and this situation relatively is arranged in the scheme of occasion of this example of inside of electro-magnet magnetic yoke 17a at permanent magnet 20, can reduce the magnetic leakage flux, the attraction force that can make permanent magnet 20 easily is zero.
In addition, the variance ratio of the attraction force of the power consumption of the electromagnet 17 of built-in permanent magnet 20 (plotted curve A) is less than the electromagnet 17 (plotted curve B) of monomer, and still, its magnetic flux bleed-through by the part of permanent magnet 20 causes.
In addition, in the scheme of the above-mentioned electromagnet 17 that is built-in with permanent magnet 20, in the electro-magnet magnetic yoke 17a of permanent magnet 20 is set, formation such as, the occasion of the flange of location usefulness, because because of the magnetic flux bleed-through of flange portion, attraction force reduces, be provided with so preferably the section of yoke 17a and the face of permanent magnet 20 are the mode that plane shape contacts.In addition, best, according to the mode of the influence that can reduce flux leakage, be shape for lugs with the part of 20 yoke 17a that contact of permanent magnet.In addition, best, vertically permanent magnet 20 is magnetized, still, also can form the position that permanent magnet 20 is set by change, adopt the scheme of the permanent magnet 20 of diametrical magnetization.
Like this, by the electromagnet 17 built-in permanent magnets 20 that make a side, enlarge the electromagnet gap,, still can remain on the magnitude relationship of above-mentioned (2) formula that the explanation of the 1st example provides even like this under the condition of the bearing prepressing force of the light load of high speed rotating zone the best.Consequently, owing to can prevent at the control frequency band, the situation that the phase delay of mechanical system is 180 °, even so under the situation of effect maximum load, still can make the controlling object of controller 19 stable, as the Fig. 2 that in the explanation of the 1st example, provides, can be proportionally or proportional integral constitute the circuit structure of controller 19 simply.
Like this, in the magnetic bearing device of the 3rd example that is applicable to turbine assembly 5, the magnitude relationship of the negative rigidity of the spring of above-mentioned synthetic spring and electromagnet 17 is set according to the mode of above-mentioned (2) formula that provides in the explanation of the 1st example, in addition, inside at the yoke 17a of electromagnet 17 is provided with permanent magnet 20, thus, enlarge the electromagnet gap, like this, even can form under the situation of effect maximum load, the scheme that the controlling object of controller 19 is still stable, the circuit structure that can form controller 19 is the simple proposal of ratio or proportional integral.
Fig. 7 and Fig. 8 represent the 4th example of the present invention.This example is at the magnetic bearing device of the 3rd example shown in Figure 4, and the scheme image pattern 8 of the electromagnet 17 of built-in permanent magnet 20 constitutes like that.Fig. 8 represent along the VI-VI line of Fig. 7 to looking sectional view, permanent magnet 20 on each cutting plate 20A～20D of permanent magnet 20, is wound with coil 17b for along the circumferential direction being divided into the ring-type of a plurality of (4) here respectively, thus, center on cutting plate 20A～20D by coil 17b.Other scheme is identical with the occasion of the 3rd example of Fig. 4.
The occasion that constitutes like this at the electromagnet 17 of built-in permanent magnet 20, owing to can directly the magnetic field that is produced by coil 17b be put on the permanent magnet 20, so can reduce the magnetic flux bleed-through of permanent magnet 20, can good efficiency reduce the attraction force of permanent magnet 20.In addition, because permanent magnet 20 is a composite structure, so its carrying easily.
But, in this scheme, be difficult to effectively adopt the space, permanent magnet 20 and coil 17b are set.If such as, in this occasion, if realize with the 3rd example of image pattern 4 such, inside at yoke 17a, the identical attraction force performance of electromagnet 17 of scheme of the annular permanent 20 of one is set, and then the thickness of permanent magnet 20 increases, thus, magnetic flux bleed-through increases, and the power consumption that is used to reduce the coil 17b of the attraction force that permanent magnet 20 produces increases.
Below in conjunction with Fig. 9～Figure 12,, the 5th example of the present invention is described with the Fig. 2 that in the explanation of the 1st example, provides.Fig. 9 represents to assemble the sectional view of turbine assembly 5 of the magnetic bearing device of this example.In this example, the aspect common with the 1st and the 3rd example adopts same label in the drawings, omits the explanation to it.
The scheme of turbine assembly of magnetic bearing device of assembling the 5th example is identical with the 3rd example, and difference is to use electromagnet selectively as the following describes.In addition, in this example, shown in the image pattern 9 like that, divide the electromagnet 17B of the monomer of the electromagnet 17A of built-in permanent magnet and not built-in permanent magnet 20, the label of electromagnet 17 is described.
In the magnetic bearing device of this 5th example, in order to remain on the magnitude relationship of above-mentioned (2) formula that provides in the 1st example, in two electromagnet 17A, the 17B of clamping thrust plate 13a, bear a side of excessive axial load electromagnet (such as, here with sensor 18 in abutting connection with and the electromagnet 17A of the side that is provided with) the inside of yoke 17a, permanent magnet 20 is set, thus, enlarges this electromagnet gap.In Fig. 9, in order to reduce the magnetic leakage flux of permanent magnet 20, inside at the yoke 17a of the outside diameter of the coil 17b of electromagnet 17A, setting is the annular permanent 20 with the concentric one of main shaft 13, but, also can be shown in the sectional view of the Fig. 8 that illustrates at the 4th example, permanent magnet 20 is and along the circumferential direction is divided into a plurality of ring-types.
Illustrate as in the 4th example, adopting Fig. 6, to bear the electromagnet 17A of a side of excessive axial load as the electromagnet of built-in permanent magnet 20, thus, by enlarging this electromagnet gap, even be under the condition of bearing prepressing force of the light load that high speed rotating zone is best, still can remain on the magnitude relationship of above-mentioned (2) formula that the explanation of the 1st example provides.Consequently, can prevent that the situation that the phase delay of mechanical system is 180 ° is even have in effect under the situation of excessive axial load at the control frequency band, the controlling object of controller 19 can be stablized, and the circuit structure of controller 19 can be reduced to the type of ratio or proportional integral.
Figure 10 is illustrated in by the column plotted curve and with the occasion of above-mentioned two electromagnet 17A, 17B, axial load is the power consumption of the electromagnet part of underload, shoulder load and busy hour.In addition, two electromagnet that Figure 11 is illustrated in clamping thrust plate 13a by the column plotted curve adopt the occasion of the electromagnet 17A of built-in permanent magnet 20, and axial load is the power consumption of the electromagnet part of underload, shoulder load and busy hour.In addition, two electromagnet that Figure 12 is illustrated in clamping thrust plate 13a by the column plotted curve adopt the occasion of the electromagnet 17B of not built-in permanent magnets 20, and axial load is the power consumption of the electromagnet part of underload, shoulder load and busy hour.
As according to Figure 11 and clear, adopt the occasion of the electromagnet 17A of built-in permanent magnet 20 at two electromagnet, owing to act on the attraction force of the permanent magnet 20 of the inside that is arranged at electro-magnet magnetic yoke 17a, event is compared with the occasion of Fig. 6 of the electromagnet 17B of the monomer of two not built-in permanent magnets 20 of electromagnet employing, can reduce the maximum axial load coil current of outer added-time, the load capacity of power supply increases.But, on the other hand, in the example of Figure 11, axial load must be in the light load zone, and according to mode impressed current on electromagnet coil of the control force that reduces magnetic bearing, the attraction force of permanent magnet 20 is entirely zero, in this occasion, the power consumption of electromagnet coil increases, and heating increases.
So, in this magnetic bearing device, as scheme by electromagnet 17A with the electromagnet 17B clamping thrust plate 13a of the monomer of not built-in permanent magnet 20 of built-in permanent magnet 20 as described above, in the light load zone of axial load, and with two electromagnet 17A, 17B.In this occasion, electromagnet 17B for not built-in permanent magnet 20, do not produce the magnetic flux bleed-through of the part of the such permanent magnet 20 of the occasion of electromagnet 17A, thus, can increase the variance ratio (with reference to the Fig. 6 that in the 4th form of implementation, illustrates) of the relative power consumption of attraction force, but image pattern 10 is such, reduces the power consumption as the integral body of two electromagnet 17A, 17B.In addition, the load area of the axial load beyond in the light load zone only adopts the electromagnet 17A of built-in permanent magnet 20.The selection of such electromagnet 17A, 17B is used by controller 19 controls.
Like this, in this magnetic bearing device, as the electromagnet 17B of the electromagnet 17A that passes through built-in permanent magnet 20 with the monomer of not built-in permanent magnet 20, the scheme of clamping thrust plate 13a, with regional also with two electromagnet 17A in the light load of axial load, 17B, thus, adopt the occasion (with reference to Figure 12) of electromagnet 17B of the monomer of not built-in permanent magnet 20 with two electromagnet of clamping thrust plate 13a, two electromagnet of clamping thrust plate 13a adopt the occasion (with reference to Figure 11) of the electromagnet 17A of built-in permanent magnet 20 to compare, the electromagnet 17A in the actuating range that can reduce axial load the biglyyest and acted on, the power consumption of 17B.
The turbine assembly 5 of assembling the magnetic bearing device of the 1st～the 5th form of implementation be applicable to such as, air cycle refrigerating/cooling system, according to can be by the heat exchanger (illustrating in conjunction with Figure 13 in the back) of back level, the mode of the air that constitutes the cooling medium being carried out heat exchange with good efficiency, compress by compressor 6, temperature rises, in addition, the air of the above-mentioned cools down by back level is by expansion turbine 7, be cooled to target temperature by heat insulation expansion, such as ,-30 ℃～-60 ℃ extremely low temperature is used its discharge.
In such use-case, in this turbine assembly 5, compressor blade 6a and turbine bucket 7a are installed on the common main shaft 13, by the power that produces by turbine bucket 7a, Driven Compressor blade 6a, thus, power source is unwanted, be compact structure, can good efficiency cool off.
In addition, in the 1st～the 5th example, compressor blade 6a and turbine bucket 7a be embedded in the common main shaft 13 of thrust plate 13a on, by the power that produces by turbine bucket 7a, in the turbine assembly 5 of the compression-expansion turbine system of formation Driven Compressor blade 6a, the magnetic bearing device of said structure is applicable to the supporting of main shaft 13, thus, keep the gap d 1 that is fit to, d2 of each blade 6a, 7a and obtain the stable high speed rotating of main shaft 13, and the long durability of bearing 15,16 improves, the raising in life-span.
That is,, must keep gap d 1, the d2 of each blade 6a, 7a and shell 6b, 7b with small degree in order to ensure the compression of turbine assembly 5, the efficient of expansion.Such as, being applicable to the occasion of air cycle refrigerating/cooling system at this turbine assembly 5, this efficient guarantees it is important.Relative this situation, because supporting spindle 13 by the bearing 15,16 of rolling form, so,, micro-gap d1, the d2 of each blade 6a, 7a and shell 6b, 7b can be kept certain to limit the axial position of main shaft 13 to a certain degree by the limitation function of the axial position that rolling bearing had.
But, on the main shaft 13 of turbine assembly 5, the pressure by acting on the air on each blade 6a, 7a etc., effect thrust.In addition, in the turbine assembly 5 that in air cooling system, is adopted, be formed on 1 minute during, such as, 8～100,000 rotations of changeing very at a high speed.Thus, if act on above-mentioned thrust on the rolling bearing 15,16 of swivel bearing main shaft 13, then the long durability of bearing 15,16 reduces.
Because the 1st～the 5th example supports above-mentioned thrust by electromagnet 17 (17A, 17B), so when can suppress the increase of torque, alleviate the thrust on the rolling bearing 15,16 of the supporting usefulness that acts on main shaft 13 by non-contact.In this occasion, because sensor 18 is set, it detects by the air in compressor 6 and the expansion turbine 7, acts on the thrust on the main shaft 13; Controller 19, this controller 19 are controlled the supporting force of above-mentioned electromagnet 17 (17A, 17B) corresponding to the output of this sensor 18, so can at the state that is suitable for most thrust, adopt rolling bearing 15,16 corresponding to this bearing type.
Particularly and since sensor 18 be arranged at bearing 16 near, so can directly measure the thrust that acts on the bearing 16 that becomes problem, it is good that it measures precision, can carry out the control of the thrust of precision.
Figure 13 represents to adopt the scheme of integral body of air cycle refrigerating/cooling system of the turbine assembly 5 of above-mentioned 1 5th examples.The system of this air cycle refrigerating/cooling system for directly the air in the space 10 that is cooled of freezer etc. being cooled off as refrigeration agent has and is taken into the air circulation path 1 of mouthful 1a to exhaust port 1b from the air that is opened on the space 10 that is cooled respectively.In this air circulation path 1, set gradually the expansion turbine 7 of compressor the 6, the 2nd heat exchanger 8, intermediate heat exchanger 9 and the above-mentioned turbine assembly 5 of precompression mechanism the 2, the 1st heat exchanger 3, the freezing cooling usefulness of air circulation turbine assembly 5.Intermediate heat exchanger 9 is in the inside of above-mentioned air circulation path 1, be taken into mouthful 1a near the inflow air and the air that heats up, cool off of the compression by the back level between carry out heat exchange, be taken near the inside of the air of mouthful 1a by heat exchanger 9a.
Precompression mechanism 2 is made of blower etc., starts by motor 2a.The 1st heat exchanger 3 and the 2nd heat exchanger 8 have respectively makes cooling medium circuit heat exchanger 3a, 8a, between the cooling medium of the water in heat exchanger 3a, 8a etc. and the air of air circulation path 1, carries out heat exchange.Each heat exchanger 3a, 8a connect by Guan Eryu cooling tower 11, and the cooling medium that heat up by heat exchange cool off by cooling tower 11.
This air cycle refrigerating/cooling system remains on the system of 0 ℃～-60 ℃ of degree for the space 10 that will be cooled, and flows into being taken among mouthful 1a of air circulation path 1 from the air of 1 air pressure of 10,0 ℃～-60 ℃ of degree in space that are cooled.In addition, the temperature that provides below and the numerical value of air pressure are an example of special purpose.Inflow is taken into air among mouthful 1a is used for the back level of air circulation path 1 by intermediate heat exchanger 9 the cooling of air, is warmed up to 30 ℃.The air that heats up is compressed to 1.4 air pressure at the state of 1 air pressure by precompression mechanism 2, is warmed up to 70 ℃ by this compression.Because the 1st heat exchanger 3 can cool off 70 ℃ the air that heats up, so, be cooled to 40 ℃ even, still can good efficiency cool off at the cold water of normal temperature degree.
Cool off by heat exchange 40 ℃, the air of 1.4 air pressure are compressed to 1.8 air pressure by the compressor 6 of turbine assembly 5, are being warmed up to 70 ℃ state by this compression, are cooled to 40 ℃ by the 2nd heat exchanger 8.This air of 40 ℃ arrives-20 ℃ by intermediate heat exchanger 9 by-30 ℃ air coolings.For air pressure, keep 1.8 air pressure of discharging from compressor 6.
By intermediate heat exchanger 9 be cooled to-20 ℃ air by turbine assembly 5 expansion turbine 7 and heat insulation expansion is cooled to-55 ℃, be discharged to the space 10 that is cooled from exhaust port 1b.This air cycle refrigerating/cooling system carries out such freeze cycle.
In this air cycle refrigerating/cooling system, in turbine assembly 5, the gap d 1, the d2 that are fit to that keep each blade 6a, 7a, obtain the stable high speed rotating of main shaft 13, and the long durability of bearing 15,16 improves, the life-span raising, thus, because the long durability of bearing 15,16 improves, the integral body of turbine assembly 5, and then the whole reliability of air cycle refrigerating/cooling system improves.Like this, improve owing to constitute main shaft bearing 15,16 stable high speed rotating, long durability, the reliabilities of turbine assembly 5 of the weak link of air cycle refrigerating/cooling system, so can realize the practicability of air cycle refrigerating/cooling system.
Based on above-mentioned the 1st～the 7th magnetic bearing device, the scheme that can constitute example of the present invention is summarized as follows.
It is magnetic bearing device for (the 8th scheme), it relates to above-mentioned the 3rd scheme, and wherein, the yoke of above-mentioned electromagnet comprises the yoke part of internal side diameter and the yoke part of outside diameter, above-mentioned permanent magnet is arranged at the yoke part of these internal side diameters, or the yoke part of outside diameter.
In the occasion of the 8th scheme, can reduce the magnetic leakage flux of permanent magnet, can reduce the attraction force of permanent magnet effectively.
It is magnetic bearing device for (the 9th scheme), and it relates to the above-mentioned the 3rd or the 8th scheme, and wherein, the part of the above-mentioned yoke that contacts with the above-mentioned permanent magnet face of the yoke inside that is arranged at electromagnet is a plane shape.
In the occasion of the 9th scheme, the magnetic leakage flux of permanent magnet can be reduced equally, the attraction force of permanent magnet can be reduced effectively.
It is magnetic bearing device for (the 10th scheme), and it relates to the above-mentioned the 3rd, the 8 or the 9th scheme, and wherein, the part of the above-mentioned yoke that contacts with the above-mentioned permanent magnet face of the yoke inside that is arranged at electromagnet is a shape for lugs.
In the occasion of the 10th scheme, the magnetic leakage flux of permanent magnet can be reduced equally, the attraction force that permanent magnet produces can be reduced effectively.
It is magnetic bearing device for (the 11st scheme), and it relates to above-mentioned the 3rd, the 8th～10 scheme, and wherein, the shape of above-mentioned permanent magnet is the ring-type of one, or the ring-type of along the circumferential direction cutting apart.
That is,, then can effectively utilize the space, permanent magnet and electromagnet coil are set if permanent magnet is the ring-type of one.If permanent magnet is the ring-type of along the circumferential direction cutting apart, then its carrying easily.
Claims (5)
1. magnetic bearing device, it also uses rolling bearing and magnetic bearing, rolling bearing bears radial load, magnetic bearing bears any one or both in axial load and the bearing prepressing force, electromagnet is according to vertical with main shaft and mode that the flange shape thrust plate that is formed by the strong magnetism body that be provided with is coaxially faced non-contactly is installed on the main shaft shell, has output, the controller of control electromagnet corresponding to the sensor of the axial power of detection effect on main shaft;
Have the relation of the values of stiffness of the synthetic spring that the supporting system by rolling bearing and rolling bearing forms greater than the negative values of stiffness of electromagnet;
Inside in the yoke of above-mentioned electromagnet is provided with permanent magnet; Above-mentioned permanent magnet is arranged at the only inside of the yoke of the electromagnet of a side of above-mentioned thrust plate, in the light load zone of axial load, and uses the electromagnet that permanent magnet is arranged at the inside of yoke; With the electromagnet of the inside that this permanent magnet is arranged at yoke in the face of and be arranged at the electromagnet that does not comprise permanent magnet of the opposite side of thrust plate.
2. magnetic bearing device according to claim 1, the values of stiffness that it is characterized in that the synthetic spring that forms at the supporting system by rolling bearing and rolling bearing is that Kbrg, maximum load are that Fmax, electromagnet gap are that d, proportionality constant are the occasion of k, then has the electromagnet gap of satisfying the condition expression of being represented by following formula: d＞k * Fmax/Kbrg.
3. magnetic bearing device according to claim 1, it is characterized in that the electromagnet that above-mentioned permanent magnet is arranged at the inside of yoke is arranged on a side of bearing excessive axial load, the electromagnet that does not comprise above-mentioned permanent magnet is with the above-mentioned thrust plate of clamping, be provided with in the face of the ground mode with the electromagnet of the inside that above-mentioned permanent magnet is arranged at yoke.
4. magnetic bearing device according to claim 1, it is characterized in that compressor side blade and turbo machine lateral lobe sheet be embedded in the common main shaft of above-mentioned thrust plate on, by the power that produces by turbo machine lateral lobe sheet, in the compression-expansion turbine system of Driven Compressor lateral lobe sheet, be applicable to the supporting of above-mentioned main shaft.
5. magnetic bearing device according to claim 4, it is characterized in that the compression-expansion turbine system that is suitable for above-mentioned magnetic bearing device is applicable to relative inflow air, carry out the compression, the air cycle refrigerating/cooling system of heat insulation expansion that other the expansion turbine that comprises above-mentioned turbo machine lateral lobe sheet of cooling, above-mentioned turbine assembly of heat exchanger produces of the compressor that comprises above-mentioned compressor lateral lobe sheet of cooling, the turbine assembly of compression, the heat exchanger of precompression mechanism successively.
Applications Claiming Priority (9)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005355754A JP2007162714A (en) | 2005-12-09 | 2005-12-09 | Magnetic bearing device |
| JP2005355756A JP2007162716A (en) | 2005-12-09 | 2005-12-09 | Magnetic bearing device |
| JP355756/2005 | 2005-12-09 | ||
| JP355754/2005 | 2005-12-09 | ||
| JP355755/2005 | 2005-12-09 | ||
| JP355757/2005 | 2005-12-09 | ||
| JP2005355755A JP4942337B2 (en) | 2005-12-09 | 2005-12-09 | Magnetic bearing device |
| JP2005355757A JP2007162717A (en) | 2005-12-09 | 2005-12-09 | Magnetic bearing device |
| PCT/JP2006/322559 WO2007066473A1 (en) | 2005-12-09 | 2006-11-13 | Magnetic bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101326377A CN101326377A (en) | 2008-12-17 |
| CN101326377B true CN101326377B (en) | 2010-05-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN2006800459209A Expired - Fee Related CN101326377B (en) | 2005-12-09 | 2006-11-13 | Magnetic bearing device |
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| JP (1) | JP2007162714A (en) |
| CN (1) | CN101326377B (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2010145704A1 (en) * | 2009-06-18 | 2010-12-23 | Sulzer Metaplas Gmbh | Protective coating, a coated member having a protective coating as well as method for producing a protective coating |
| EP2677640B1 (en) * | 2012-06-22 | 2014-10-01 | Skf Magnetic Mechatronics | Turbocharger embedding an electrical machine with permanent magnets |
| ITUA20161810A1 (en) * | 2016-03-18 | 2017-09-18 | Nuovo Pignone Tecnologie Srl | MAGNETIC BEARING FOR A TURBOMACCHINA |
| CN105817952B (en) * | 2016-05-11 | 2018-01-19 | 西安交通大学 | A kind of online main shaft based on mixing supporting electric main shaft collides and cutter fractures monitoring system and method |
| IT201700067928A1 (en) * | 2017-06-19 | 2018-12-19 | Nuovo Pignone Tecnologie Srl | CONTROL SYSTEM FOR TURBOMACCHINA FOR DANGEROUS AREAS |
| CN110486382B (en) * | 2019-08-30 | 2021-04-09 | 上海大学 | Radial-axial permanent magnetic bearing system device |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5555745A (en) * | 1995-04-05 | 1996-09-17 | Rotoflow Corporation | Refrigeration system |
| US5836739A (en) * | 1995-03-17 | 1998-11-17 | Rolls-Royce Plc | Gas turbine engine |
-
2005
- 2005-12-09 JP JP2005355754A patent/JP2007162714A/en active Pending
-
2006
- 2006-11-13 CN CN2006800459209A patent/CN101326377B/en not_active Expired - Fee Related
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5836739A (en) * | 1995-03-17 | 1998-11-17 | Rolls-Royce Plc | Gas turbine engine |
| US5555745A (en) * | 1995-04-05 | 1996-09-17 | Rotoflow Corporation | Refrigeration system |
Non-Patent Citations (3)
| Title |
|---|
| JP特开2003-65621A 2003.03.05 |
| JP特开2005-240963A 2005.09.08 |
| 全文. |
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| CN101326377A (en) | 2008-12-17 |
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