• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The invention proposes a magnetic bearing system (1) comprising an axial bearing rotary wheel (2) arranged in such a way as to be able to interact magnetically with at least one fixed axial stop (3, 4). The system comprises a cooling fluid path (31) arranged to send the flow to the flywheel (2) in a flow direction lying in a substantially radial plane with respect to the axis (XX ') of rotation of the steering wheel (2).
    公开号:FR3022963A1
    申请号:FR1456060
    申请日:2014-06-27
    公开日:2016-01-01
    发明作者:Denis Guillaume Guenard
    申请人:Thermodyn SAS；
    IPC主号:
    专利说明:

    [0001] The invention relates to fluid-cooled bearing systems, and more particularly to systems comprising an axial magnetic bearing cooled by a fluid flow. Typically, in such a bearing, a fluid flow, for example a gas flow, is injected into one or into air gaps separating a rotating flywheel from the axial bearing, and one or more fixed stops of the axial bearing. The flow of gas must be sufficient to evacuate both the calories generated by the magnetic induction phenomena, and the calories generated by the viscous friction fluid at the air gap. Ventilation losses are the last type of loss.
    [0002] When the bearing system is part of a rotating machine such as a turbine or a compressor, the high flow rates of gas required for cooling sometimes lead to setting up a cooling fluid circuit configured to cool not only the bearing system but to cool other machine parts as well. This cooling circuit can be organized internally to the machine, for example using the main fluid circulating in the rotating machine and the pressure differences naturally existing within this machine, or can be organized separately using a circuit dedicated cooling using possibly another fluid (eg but not exclusively, air) and a dedicated fluid flow generation system. In all cases, the cooling flow directly generates an economic loss, either through a loss of efficiency of the turbomachine (internal system), or by the cost related to the investment and use of the engine. external cooling system.
    [0003] In order to reduce the cost of cooling, it is desired to be able to reduce the flow rates of cooling fluid while continuing to ensure the same operating temperatures of the elements of the bearing or the bearing system.
    [0004] The object of the invention is to propose a bearing, or a bearing system, cooled by a fluid circulation system which makes it possible to ensure efficient cooling of the bearing, ie which makes it possible to evacuate the calories generated by the Magnetic, electrical and ventilation losses, while calling for a reduced flow of coolant. The invention proposes to reduce the need for cooling by reducing ventilation losses. In general, the loss of ventilation corresponds to the energy yielded by the rotating flywheel to the cooling fluid. This energy can be positive negative or zero. - If the local speed of the steering wheel is higher than the fluid speed, the flywheel causes the fluid to rotate. The fluid is warmed up. The greater the speed difference between fluid and flywheel, the greater the energy lost. - If the local velocity of the fluid is identical to that of the steering wheel, there is no friction and no loss by ventilation. - If the speed of the fluid is greater than, and in the same direction as the speed of the steering wheel, the fluid drives the steering wheel by giving up energy. It can be deduced that the loss of ventilation can be limited or canceled by reducing the speed difference existing at any point between the thrust wheel and the coolant.
    [0005] The general principle of the invention is to inject the cooling fluid, preferably at high speed, in the direction of rotation (tangential direction) of the stop, so as to minimize friction losses. By high speed is meant a tangential fluid velocity representing 50% to 150% of the tangential velocity of the abutment at the point of the stop passing in front of the injection point. Simple considerations of conservation of the kinetic moment of the injected fluid show in particular that for a given injection speed, it is more effective for the reduction of the frictional loss to inject the fluid at the periphery of the flywheel rather than towards the internal diameter. To this end, the invention proposes a magnetic bearing system comprising an axial bearing rotary flywheel arranged in such a way as to be able to interact magnetically with at least one fixed axial abutment. The system comprises a coolant path arranged to send the flow of coolant fluid to the steering wheel in a direction of flow in a plane substantially radial to the axis of rotation of the steering wheel. The fluid is injected into the bearing system so that the fluid flows along one or more free walls of the steering wheel, in an axial air gap between the flywheel and one or more axial stops.
    [0006] According to a preferred embodiment, the fluid is sent towards a peripheral circumferential surface of the steering wheel. According to an alternative embodiment, the fluid is sent towards the peripheral circumferential surface so as to impact it. According to another variant embodiment, the fluid is sent in the direction of the peripheral circumferential surface so that the flow flows along a substantially radial surface contiguous to the peripheral circumferential surface. By circumferential peripheral surface is meant a surface limiting the radial extent of the steering wheel. This surface may be a cylindrical surface portion of revolution, may be a cylindrical surface portion generated by a non-circular profile, or may be a non-cylindrical surface portion, for example a toric surface portion on which blades are assembled.
    [0007] In the present description, the term "radial surface" means a plane surface generated by lines perpendicular to the axis of the steering wheel and all passing through the same point of the axis. Axial direction means a direction of line parallel to the axis. Axial surface means a surface portion generated by lines that are all parallel to the axis. Such a surface is actually a surface or a cylindrical surface portion. It is possible to envisage variant embodiments in which the flow of fluid is injected, for example through a stop, into the air gap between the steering wheel and the stop, without sweeping the most peripheral part of the steering wheel. The injection direction of the flow is then configured to be substantially in the plane of the gap. For example, the injection direction of the flow forms an angle with the axis of the steering wheel which is between 70 ° and 110 °, and preferably between 80 ° and 100 °. According to an advantageous embodiment, the cooling flow is sent on the steering wheel so that, in at least one point of impact of the flux on the steering wheel, the speed component of the flow which is perpendicular to the direction radial, is greater than or equal to half the linear speed of rotation of the steering wheel at this point of impact, and preferably greater than or equal to 0.7 times the linear speed of rotation of the steering wheel at this point of impact. According to an advantageous embodiment, particularly when the flux is sent on a peripheral circumferential surface of the flywheel, the tangential velocity of the fluid flow (ie the speed perpendicular to the radial direction) is greater than the linear speed of rotation at the point of rotation. impact, so as not only to limit the fluid friction generated by the cooling flow, but also to provide mechanical energy of rotation to the steering wheel. By point of impact, is meant here a meeting point between the fluid path and the surface of the steering wheel. The tangential velocity of the fluid flow may be lower than the local speed of rotation of the flywheel, especially in the case where the fluid flow is injected by centering it on the gap between the flywheel and the stop. The direction of the fluid flow may be imposed by a direction of pipe or drilling bringing the fluid to the steering wheel, for example through a flow guide piece. The desired total speed of the fluid flow may be imposed in particular by the section of pipes or fluid feed bores, by the length of these bores, and by the fluid pressure imposed at the inlet of these bores or pipes. Advantageously, the magnetic bearing system comprises at least one fluid flow guide piece traversed by at least one piercing, the piercing opening in the vicinity of a peripheral circumferential surface of the flywheel. The piercing may be configured to send the coolant flow to the flywheel in an incidence direction that is perpendicular or oblique to the local radial direction in the impact zone of the cooling flow line on the flywheel. wheel.
    [0008] By "close to the peripheral circumferential" is meant that the flow of fluid comes into contact with the peripheral circumferential surface or at least one edge of this surface. The angle between the direction of incidence of the flow and the local radial direction of the steering wheel may for example be estimated as a first approximation by drawing at least one line tangent to a guide surface at the outlet of a bore of the guide piece, taking the meeting point of this line with the steering wheel, and estimating the angle between the tangent line and the radial direction of the wheel passing through the meeting point.
    [0009] According to an advantageous embodiment, the bore is disposed in a direction substantially tangential to a peripheral circumferential surface of the flywheel. If the peripheral surface of the flywheel is smooth, it can be considered that the direction of the drilling is substantially tangential if at least one line tangent to a guide surface at the outlet of a bore, is tangential to the peripheral surface of the flywheel. Advantageously, the drilling is substantially parallel to a radial plane of the steering wheel, that is to say is parallel to the plane of the air gaps bordering the steering wheel. More generally, it can be considered that the direction of the drilling is substantially tangential to the steering wheel if at least one line tangent to a guide surface at the outlet of a bore, forms an angle of between 45 ° and 90 ° relative to the radial direction of the steering wheel at a point of the steering wheel intercepted by the tangent line.
    [0010] According to a preferred embodiment, the flow guide piece surrounds the steering wheel. The flow guide piece is preferably traversed by several bores, angularly distributed around the workpiece and opening each near the steering wheel. According to a first embodiment, the bores are substantially centered in the middle of the axial width of the steering wheel. According to a second embodiment, at least one group of bores are substantially centered on an air gap, the gap separating the flywheel and an axial stop associated with the steering wheel. Associated with the steering wheel is an axial stop placed so as to interact magnetically with the steering wheel. Advantageously, the bearing system comprises a steering wheel configured to interact magnetically with a first and a second axial abutment, placed respectively on either side of the steering wheel. The flow guide piece may then comprise two groups of holes, a first group of holes being substantially axially centered on the air gap between the flywheel and the first axial stop, and a second group of holes being substantially centered axially on the air gap. between the steering wheel the second axial stop. According to an advantageous embodiment, the magnetic bearing system comprises a cavity around the guide piece, able to be supplied with pressurized gas, and into which at least the radially outer ends of two of the bores of the guide piece open. of flow. The peripheral circumferential surface of the steering wheel may be smooth in the simplest case, or provided with reliefs, or provided with blades extending at the periphery of the steering wheel in an axial direction. These reliefs or blades form protuberances in a radial direction of the steering wheel.
    [0011] In some embodiments, the reliefs or blades may extend axially just over a portion of the axial thickness of the flywheel. In other embodiments, the reliefs or blades may extend axially over the entire axial thickness of the flywheel. It is also possible to envisage variant embodiments in which reliefs are provided on at least one radial face of the steering wheel, the reliefs extending at least partly in a radial direction of the steering wheel. These reliefs and / or these blades formed on the peripheral circumferential surface and / or formed on the radial faces of the flywheel inside the air gap of the steering wheel, are configured to facilitate the drive in rotation of the flywheel by the fluid flow cooling, especially if the local tangential velocity of the fluidi.e. the tangential velocity of the fluid with respect to an orthoradial direction of the flywheel is greater than the speed of rotation of the flywheel in contact with the fluid. According to another aspect, the invention proposes a method of cooling a rotating magnetic bearing wheel arranged to turn facing a fixed axial abutment, or arranged to rotate between two fixed axial abutments, in which a fluid flow is injected. cooling to the steering wheel in a direction of flow in a substantially radial plane relative to the axis of rotation of the steering wheel. At least a portion of the cooling fluid flowing in an air gap between the flywheel and an axial stop may be sensed and this flow portion may be passed through a radial bearing so as to cool the radial bearing. The capture can be performed for example by communicating a radial clearance between the wheel and the stop, communicating itself with the gap, and a radial clearance between a fixed portion and a rotatable portion of a Radial magnetic bearing located nearby. It is also possible to communicate the radial clearance between flywheel and stop, and cooling channels passing through a fixed part of the radial magnetic bearing. Cooling fluid discharge lines are of course arranged outwardly of the radial magnetic bearing, on the axial side opposite to the incoming fluid inlet of the axial bearing, in order to allow the circulation of the cooling fluid through the bearing. radial. The radial magnetic bearing may be a magnetic bearing forming part of the same mechanical subassembly as the axial magnetic bearing. According to another variant embodiment, the radial magnetic bearing may be a radial bearing situated at a distance from the axial magnetic bearing, that is to say a radial bearing separated from the axial bearing by a third rotating member, for example a radial bearing belonging to at a compression stage of a rotating machine. Other objects, features and advantages of the invention will appear on reading the following description, given solely by way of non-limiting example, and with reference to the appended figures, in which: FIG. 1 is a diagrammatic view of longitudinal section of a bearing system according to the invention, - Figure 2 is a simplified cross-sectional view of a subassembly belonging to a bearing according to the invention, - Figure 3 is a simplified cross-sectional view. of a subassembly belonging to another bearing according to the invention, - Figure 4 is a simplified cross-sectional view of yet another bearing according to the invention, and - Figure 5 is a simplified longitudinal sectional view. of a bearing variant according to the invention.
    [0012] As illustrated in FIG. 1, a magnetic bearing system 1 for a rotating machine according to the invention is assembled on a shaft 5 having a geometric axis XX 'and comprises a rotary flywheel 2 assembled on the shaft 5, integral with rotation of the shaft 5 and maintained on the shaft 5 for example by means of a nut 11, comprises a first axial abutment 3 and a second axial abutment 4 integral with a housing 9 of the bearing system, the housing 9 being fixed. The system comprises at least one central radial clearance zone 32, defining a radial clearance between the shaft 5 or between a central portion of the flywheel 2 surrounding the shaft 5, and stator elements of the magnetic bearing system 1, by For example, a stop 3 or 4. These zones 32 allow non-contact rotational movement between the shaft + flywheel assembly and the stator portions surrounding the shaft in the vicinity of the flywheel. These zones 32 furthermore make it possible, by means of gas pipes opening into these zones, to evacuate gases flowing in the air gaps 21 and 22. The stops 3 and 4 are arranged in the immediate vicinity of the flywheel 2. The stops 3 and 4 are respectively axially separated from the flywheel 2 by a first gap 21 and a second gap 22.
    [0013] The first abutment 3 and the second abutment 4 comprise electrical coils for generating respectively a first and a second magnetic field axially attracting the flywheel 2 respectively to the first axial abutment 3 and to the second axial abutment 4. The balance between the two attraction forces makes it possible to maintain axially the flywheel 3 and thus the shaft 5 in an axial position determined with respect to the housing 9 of the magnetic bearing system. The housing 9 is here composed of several parts 9a, 9b, 9c, 9d of housing but could also be a one-piece housing or composed of a different number of housing elements. In the illustrated example, one of the housing parts 9c and an attached axial shim 17 respectively hold the second axial abutment 4 and the first axial abutment 3 in an axial position determined relative to the housing 9.
    [0014] The casing 9 is pierced with a fluid supply channel 8 which opens into a pressurization space 6 surrounding the outer periphery of the flywheel 2. This pressurization space 6 is separated radially by a flow guide piece 7, an immediate environment space 23 of the steering wheel, or radial gap between the steering wheel and the flow guide part 7. The immediate environment space 23 of the steering wheel defines a volume of gas in which the outer circumference of the steering wheel 9 In the example illustrated, this volume also bathes at least part of the outer circumferences of the first axial abutment 3 and the second axial abutment 4. This immediate environment space 23 also communicates with the first air gap 21 and the second air gap 21. gap 22.
    [0015] The flow guide piece 7 channels the fluid present in the pressurizing space 6 to allow this fluid to flow to the space 23 through one or more bores 20 of the flow guide piece. The holes 20 direct the flow of fluid from the pressurizing space 6 to the flywheel 2, in a centripetal direction substantially within a radial plane. Axial direction means in the description a direction parallel to the axis of rotation XX 'of the machine. Radial direction means a direction perpendicular to the axis XX 'and passing through this axis XX'. The flow 31 of cooling fluid is here represented by black arrows. This flow 31 passes through the fluid supply channel 8 and the fluid guide piece 7 by the bore or holes 20, and impinges the flywheel 2, on the one hand on a peripheral circumferential surface 24 of the flywheel, and on the other hand. on the other hand at the radial surfaces 25 and 26 of the steering wheel. The radial surfaces 25 and 26 of the flywheel respectively axially limit the first air gap 21 and the second air gap 22. It is possible to envisage variant embodiments in which the cooling flow arrives on the steering wheel in a direction lying in a radial plane, impacting either only the peripheral circumferential surface 24, or only one or two radial surfaces 25, 26 of the steering wheel. In the latter case, the flow of cooling fluid is preferably directed so as to impact with a comparable flow each of the two radial surfaces, in order to change as little as possible the axial balance of the flywheel. Regardless of the impact surface on the flywheel 2, the coolant flow 31 flows along the radial surfaces 25 and 26 of the flywheel 2 until reaching the zones 32 of central radial clearance. From the central radial clearance zones 32, the cooling fluid can be channeled to be fed to other members to be cooled.
    [0016] In the illustrated example, the flow of fluid flowing on one of the radial surfaces of the flywheel 2, here the fluid flowing on the left side, that is to say on the surface 25 of the steering wheel, is then directed to through a radial magnetic bearing 12 belonging to the same rotating machine as the axial magnetic bearing 1, in order to cool this radial magnetic bearing. The rotating machine may be a turbine or a compressor handling a gas or a fluid. The cooling fluid can be fed from the axial bearing 1 to a radial bearing flat to the same stage of compression or expansion as the axial bearing 1, or can be sent to another stage of the rotating machine. As the coolant flow is sent, as described later, on at least one surface of the flywheel with at least one non-zero velocity component tangential to the surface, and furthermore, according to a preferred embodiment, the relative tangential velocity of the fluid relative to the surface is less than the absolute velocity, in a fixed reference linked to the casing 9, the pressure drops of the cooling fluid in contact with the flywheel 2 are less than in conventional embodiments where the fluid is sent on one of the radial surfaces of the steering wheel, in a substantially axial direction. In addition, the coolant heats up less than in a conventional embodiment of comparable flow. This lower pressure drop and lower heating can reuse the coolant more effectively to cool other organs after cooling the steering wheel 2.
    [0017] In the illustrated example, from the radial play zone 32 of the axial bearing, a portion of the cooling fluid is directed in a radial clearance 33 formed between the rotary portion 12a and the stator portion 12b of the radial bearing 12, and a part of the fluid is directed through one or more cooling channels 13 traversing in the same axial direction the stator portion of the radial bearing 12. These channels 13 are drilled only on a limited angular portion about the axis XX ', and do not form a radial clearance extending all the way around the axis XX '. The fluid having passed through the radial bearing 12 can then be extracted from the magnetic bearing system 1 by a fluid discharge orifice 34 passing through the casing 9. The bearing system may optionally also comprise a radial ball bearing 18 making it possible to keep a mobility of the shaft 5 with respect to the stator housing 9 during the phases in which the radial magnetic bearing 12 is deactivated. As the fluid flow 31 arrives on the flywheel 2 of the axial bearing in a direction which is substantially radial, the effect of fluid friction at the air gaps 21 and 22 is reduced. In addition, if the direction of arrival of the fluid through the hole or holes 20 is configured to be directed obliquely to the local normal to the peripheral circumferential surface 24 of the flywheel, then the pressure of the flow 31 of coolant can contribute to the rotation of the flywheel 2, instead of generating fluid friction forces which tend instead to brake the steering wheel 2 and to release additional calories by friction fluid. It is preferable for this reason that in at least some cooling fluid impact points on the flywheel 2, the orthoradial velocity of the cooling fluid is greater than or equal to the local linear speed of the point impacted on the flywheel 2 by the fluid. cooling. The points concerned by this speed ratio may be either points located on the peripheral circumferential surface 24 of the steering wheel, or points located on the first radial surface 25 or located on the second radial surface 26 of the steering wheel.
    [0018] FIG. 2 schematically illustrates a section in a radial plane of a flow guide member 7 according to the invention and a steering wheel 2 according to the invention. FIG. 2 shows elements that are common to FIG. 1, the same elements being designated by the same references. The border between the wheel 2 and the shaft 5 is not shown in this figure. The flow guide piece 7 is here traversed by a plurality of bores 20 each extending symmetrically on either side of a mean radial plane corresponding for example to the plane of the figure. Each bore 20 forms a substantially rectilinear channel, the direction of the channel corresponding substantially to the direction of incidence, denoted F, of the flow of cooling fluid leaving this channel in the direction of the flywheel 2. The direction F is here substantially tangent to the peripheral circumferential surface 24 of the steering wheel.
    [0019] Thus, the speed of the cooling fluid impacting the flywheel 2 can effectively contribute to transmitting a moment of rotation to the steering wheel 2. It is assumed, in the example illustrated in FIG. 2, that the usual direction of rotation of the steering wheel 2 is the clockwise. It is possible to define an angle of incidence of the cooling flow on a point M of the steering wheel 2, such as the angle between the arrival direction F of the flow on the steering wheel, and a radial direction Rad (M) passing through the point M and the axis XX '. The flow of cooling fluid arriving through the bores 20 can flow, on the one hand and initially, around the peripheral circumferential surface 24 of the steering wheel and secondly, directly or in a second step, along radial surfaces 25 and 26 of the steering wheel towards the axis XX ', as shown in Figure 2, the duplication of the arrow 31 at the point of impact M on the steering wheel. As illustrated in FIG. 2, the circumferential circumferential surface 24 of the flywheel may have reliefs, roughnesses or ridges 27 improving the driving effect in rotation of the steering wheel under the effect of the thrust of the fluid flow of the flywheel. incoming cooling with a tangential speed component on the steering wheel. Such reliefs, roughnesses or grooves may also be formed on the first radial surface 25 and the second radial surface 26 of the flywheel 2, or be provided only on the radial surfaces of the flywheel 2. Reliefs on the peripheral circumferential surface 24 are however simpler to achieve so as to disturb the magnetic field lines in the steering wheel, as reliefs formed on the radial surfaces 25 or 26 of the steering wheel. In the illustrated example, the bores 20 bringing the flow of fluid towards the steering wheel 2 are angularly distributed regularly around the flywheel 2. It is possible to envisage alternative embodiments in which the bores 20 are distributed so that the distance between two successive holes forms a pattern obtained by angular offset of a basic pattern, without all the holes are equidistant from each other. According to an alternative embodiment, the bores 20 may not even be evenly distributed around the axis XX '. In an alternative embodiment, it would be possible to bring the flow of cooling fluid by a single bore or a single group of bores, all located substantially at the same angular position with respect to the flow guide piece 7.
    [0020] Figure 3 illustrates in a simplified manner, a section in a radial plane, another flow guide member 7 according to the invention and another wheel 2 according to the invention. FIG. 3 shows elements that are common to the preceding figures, the same elements being designated by the same references. In the example illustrated in FIG. 3, the peripheral surface 24 of the flywheel 2 comprises circumferential blades 28 extending radially between a circumferential minimum radius R1 of the flywheel 2 and a circumferential maximum radius R2 of the flywheel 2. The blades 28 have a geometry configured to improve the rotational drive of the flywheel 2 by a coolant flow coming through the holes 20, and impacting the peripheral circumferential surface 24 of the steering wheel in a direction F. If we take into account a point M of point of impact of the cooling flow on the flywheel 2, the angle α between the impact direction F and the radial radial direction Rad (M), is here greater than 90 °, that is to say that the F impact direction of the flow is not just tangent to the average contour of the wheel, but this direction F "points" towards the center of the wheel 2, which facilitates the flow of cooling flow along the radial surfaces of the wheel flying, the first and second gaps 21 and 22 (not shown in Figure 3), and in the direction of the evacuation of the cooling fluid. In the embodiment of FIG. 2, this value of the angle α is close to 90 °, which in turn improves the driving effect in rotation of the steering wheel.
    [0021] It is thus possible to distinguish two embodiments each having their advantages, concerning the associated geometries of the guide piece 7 and the flywheel 2. In a first variant embodiment, the direction of the bores 20 is such that the direction of the fluid flow F is tangential to a circle of axis XX 'whose radius is between a circumferential minimum radius R1 and a circumferential maximum radius R2 of the flywheel 2. The drive effect is then maximized by the fluid flow for the fluid s' flowing around the peripheral circumferential surface 24 of the steering wheel.
    [0022] In another embodiment, the direction of the holes 20 is such that a circle of axis XX 'tangential to the flow direction F has a radius less than the minimum radius R1 of the peripheral circumferential surface 24 of the flywheel. This second embodiment facilitates the flow in the air gaps 21 and 22 bordering axially the flywheel 2, and facilitates where appropriate the drive in rotation of the flywheel by the fluid friction of the cooling fluid on the radial surfaces 24 and 25 of the steering wheel. . Figures 3 and 4 are illustrations of such a second embodiment. Figure 4 illustrates in a simplified manner a third piece 7 flux guide according to the invention and a steering wheel 2 associated. In the example of FIG. 4, the steering wheel 2 is shown in front view at its first radial surface 25. This radial surface 25 is provided with lateral blades 29 facilitating the rotational drive of the steering wheel 2 by a portion of the flow of cooling fluid flowing in the first gap 21. Such blades 29 may for example be defined by a slight rib-shaped relief extending between the outer circumference of the flywheel 2 and an inner boundary of radius R3 on the radial surface of the steering wheel. The axial thickness of these blades remains moderate so as not to disturb, as far as possible, the magnetic interactions between the flywheel 2 and the axial stops 3 and 4 (not shown in Figure 4). In order to favor a cooling of the flywheel 2 by its radial faces 25 and 26, it is possible to provide, instead of a single bore 20 at each angular position of drilling, two parallel bores 20a and 20b as shown in FIG. , each of the bores 20a and 20b opening substantially facing respectively the first air gap 21 and the second gap 22. Figure 5 illustrates a simplified view, in axial section, such an embodiment. FIG. 5 shows elements that are common to the preceding figures, the same elements being designated by the same references. Two parallel bores 20a and 20b as shown in Figure 5, or a series of two bores 20a and 20b angularly distributed about the axis XX ', open substantially opposite the first air gap 21 and the second air gap 22 respectively. Example illustrated in Figure 5, the axial width (ie along the axis XX ') of each of the bores 20a and 20b is less than the axial distance between the first axial abutment 3 and the second axial abutment. In other words, the axial width of each of the bores 20a and 20b is less than the axial thickness of the flywheel 2. Each of the bores 20a and 20b is substantially centered on the first air gap 21 and on the second gap 22 respectively. embodiment in which the bores 20a and 20b are not strictly centered on the air gaps, but the two bores 20a and 20b are arranged symmetrically with respect to a median radial plane separating the two air gaps 21 and 22, and the two bores 20a. and 20b are each arranged at least partly facing one of the air gaps. With the cooling fluid circulation system according to the invention, it reduces the fluid friction heating of the coolant at the steering wheel 2 and the axial stops 3 and 4. The number of calories to be evacuated thus being reduced, the Coolant flow rate necessary to ensure a given temperature of the magnetic bearing system is also reduced. In some cases, the fact of going from a usual configuration where the injection of cooling fluid is done in an axial direction, to the configuration according to the invention with injection in a radial plane, makes it possible to halve the thermal power. to evacuate at the axial bearing.
    [0023] The gas or the cooling fluid injected at the supply channel 8 is preferably a cold fluid, for example a gas with a temperature of between 10 ° C. and 50 ° C. For typical axial bearing applications, for example an axial compressor bearing, the cooling fluid pressure at the pressurizing space 6, surrounding the flow guiding part 7, may be of the order of 2 to 3 bars. It is then possible to obtain, at the outlet of the bores 20, in the space 23 delimited outside the flow guide piece 7 and immersed in the flywheel 2, a cooling fluid pressure of, for example, between 1 and 2 bar, and a fluid flow rate of, for example, between 150 and 350 m / sec. Advantageously, the thickness of the gaps is configured so that the cooling fluid pressure arriving in the vicinity of the shaft 5 is still greater than 1 bar, for example at least greater than 1.2 bar. This overpressure with respect to the atmospheric pressure makes it possible either to let the cooling fluid escape spontaneously to the outside of the casing, or to use this fluid to cool other elements of the bearing system or other elements of the casing. an assembly integrating the bearing system. The invention is not limited to the embodiments described and can be declined in many variants. The injection channels described above as holes may not be rectilinear, and could be made by other techniques than drilling by machining, for example could be made in the foundry. The peripheral circumferential surface 24 of the steering wheel may comprise reliefs or monobloc blades with the steering wheel, or may include inserts intended to improve the "wind catch" of the peripheral surface of the steering wheel. This circumferential surface can also be smooth. It is possible to envisage variant embodiments in which the flow of gas or cooling fluid is brought in a substantially radial direction on the flywheel, this direction of arrival of the fluid not being strictly radial but for example included in an angle between 0 and 15 ° with respect to the radial direction. If this variant embodiment contributes little to driving the steering wheel in rotation, it at least reduces the fluid friction between the coolant and the steering wheel.
    [0024] The magnetic bearing system according to the invention could comprise only one axial stop associated with the steering wheel, for example in the case of systems with vertical axis of rotation. The magnetic bearing system according to the invention is particularly advantageous for systems such as pumps, turbines, or compressors, which are already cooled by a fluid flow. The magnetic bearing system according to the invention could be applied to any magnetic system intended to maintain a determined axial position of an axis of rotation of any mechanical system. The cooling fluid circuit could be dedicated solely to the cooling of an axial bearing flywheel and one or more associated stops, without the fluid being subsequently recovered to cool other elements of the bearing or the associated mechanical system. It is possible to envisage, for systems intended to operate indifferently in one or the other direction of rotation about the axis XX ', two families of injection channels 20 used alternately depending on the direction of rotation, each of families of injection channels having an angle of incidence of opposite flow relative to the flywheel 2. It is also possible boring or injection channels 20 arranged in a radial direction of the steering wheel.
    权利要求:
    Claims (10)
    [0001]
    REVENDICATIONS1. Magnetic bearing system (1) comprising a rotatable flywheel (2) axially disposed so as to magnetically interact with at least one fixed axial stop (3, 4), characterized in that the system comprises a cooling fluid path (31) arranged to send the flow to the steering wheel (2) in a flow direction (F) in a substantially radial plane relative to the axis (XX ') of rotation of the wheel (2).
    [0002]
    2. Magnetic bearing system according to claim 1, comprising at least one piece (7) for guiding the flow of fluid through at least one bore (20), the bore opening near a peripheral circumferential surface (24). of the flywheel (2), the bore (20) being configured to send the flow (31) on the flywheel (2) in an incidence direction which is perpendicular or oblique with respect to the radial direction (Rad (M)) local of the steering wheel.
    [0003]
    3. Magnetic bearing system according to claim 2, wherein the piece (7) of flow guide surrounds the flywheel (2), the flow guide piece being traversed by several bores (20), angularly distributed around the workpiece. and opening each close to the steering wheel (20) substantially at a same angle of incidence relative to the steering wheel (2).
    [0004]
    4. Bearing system according to one of claims 2 to 3, wherein the bores (20) are substantially centered in the middle of the axial width of the wheel (2).
    [0005]
    5. Bearing system according to one of claims 2 to 4, wherein at least one group of bores (20a, 20b) are substantially centered on an air gap (21, 22) separating the flywheel (2) and an axial stop ( 3,4) associated with the steering wheel.
    [0006]
    6. A bearing system according to claim 5, comprising a flywheel (2) configured to interact magnetically with a first (3) and with a second (4) axial stops placed respectively on either side of the steering wheel, the guide piece. flow device (7) comprising two groups of bores (20a, 20b), a first group of bores (20a) being substantially centered axially on the gap (21) between the flywheel (2) and the first axial stop (3), and a second group of holes (20b) being substantially axially centered on the gap (22) between the flywheel (2) and the second axial stop (4).
    [0007]
    Magnetic bearing system according to one of claims 2 to 6, wherein the peripheral circumferential surface (24) of the flywheel is provided with reliefs (27) or blades (28) extending in an axial direction (XX ' ) of the steering wheel.
    [0008]
    8. A method of cooling a rotating flywheel (2) for magnetic bearing arranged to rotate against a fixed axial abutment or between two fixed axial abutments (3, 4), in which a flow of cooling fluid (31) is injected. towards the steering wheel (2) in a direction of flow (F) lying in a substantially radial plane relative to the axis of rotation (XX ') of the steering wheel.
    [0009]
    9. A method of cooling a magnetic bearing according to the preceding claim, wherein the cooling flow (31) is sent on the steering wheel so that, in at least one point of impact (M) of the flow on the the flywheel component, the velocity component of the flow which is perpendicular to the radial direction (Rad (M)), is greater than or equal to half the linear speed of rotation of the flywheel at this point of impact (M), and preferably greater than or equal to 0.7 times the linear speed of rotation of the flywheel at that point of impact.
    [0010]
    10. A method of cooling a magnetic bearing according to one of claims 8 or 9, wherein is captured at least a portion of the cooling fluid (21, 22) flowing in an air gap between the flywheel and an axial stop (3, 4) and this flow portion is fed through a radial bearing (12) so as to cool the radial bearing (12).
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    同族专利:
    公开号 | 公开日
    SA516380599B1|2021-08-19|
    CN107076211A|2017-08-18|
    CN107076211B|2019-12-24|
    KR20170039656A|2017-04-11|
    BR112016030523A2|2017-08-22|
    CA2952533A1|2015-12-30|
    BR112016030523A8|2021-06-29|
    FR3022963B1|2016-11-11|
    US10718382B2|2020-07-21|
    JP2017522508A|2017-08-10|
    JP6765973B2|2020-10-07|
    RU2016149079A|2018-07-27|
    US20170152893A1|2017-06-01|
    KR102346384B1|2022-01-04|
    WO2015197750A1|2015-12-30|
    RU2016149079A3|2018-11-27|
    AU2015279199B2|2018-08-23|
    RU2699625C2|2019-09-06|
    AU2015279199A1|2017-01-05|
    EP3161337B1|2020-10-14|
    EP3161337A1|2017-05-03|
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    CN106402175B|2016-11-21|2019-09-03|南京磁谷科技有限公司|A kind of bearing cooling structure|
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    CN107588111A|2017-10-30|2018-01-16|南京磁谷科技有限公司|A kind of thrust disc structure of magnetic suspension rotor|
    CN109441955A|2018-12-18|2019-03-08|南京磁谷科技有限公司|A kind of magnetic axis holder structure to radiate for radial direction magnetic bearing and thrust magnetic bearing|
    CN110571971B|2019-11-06|2020-03-03|山东天瑞重工有限公司|Magnetic suspension motor with negative pressure air cooling device|
    法律状态:
    2015-06-17| PLFP| Fee payment|Year of fee payment: 2 |
    2016-01-01| PLSC| Publication of the preliminary search report|Effective date: 20160101 |
    2016-06-28| PLFP| Fee payment|Year of fee payment: 3 |
    2017-06-27| PLFP| Fee payment|Year of fee payment: 4 |
    2018-06-26| PLFP| Fee payment|Year of fee payment: 5 |
    2019-05-22| PLFP| Fee payment|Year of fee payment: 6 |
    2020-05-20| PLFP| Fee payment|Year of fee payment: 7 |
    2021-05-19| PLFP| Fee payment|Year of fee payment: 8 |
    优先权:
    申请号 | 申请日 | 专利标题
    FR1456060A|FR3022963B1|2014-06-27|2014-06-27|COOLING SYSTEM FOR MAGNETIC AXIAL BEARING|FR1456060A| FR3022963B1|2014-06-27|2014-06-27|COOLING SYSTEM FOR MAGNETIC AXIAL BEARING|
    JP2016573928A| JP6765973B2|2014-06-27|2015-06-25|Cooling system for magnetic axial bearings|
    CN201580035145.8A| CN107076211B|2014-06-27|2015-06-25|Cooling system for magnetic axial bearing|
    RU2016149079A| RU2699625C2|2014-06-27|2015-06-25|Magnetic bearing device and method of cooling flywheel of magnetic thrust bearing|
    EP15731344.6A| EP3161337B1|2014-06-27|2015-06-25|A cooling system for magnetic axial bearing|
    CA2952533A| CA2952533A1|2014-06-27|2015-06-25|A cooling system for magnetic axial bearing|
    PCT/EP2015/064349| WO2015197750A1|2014-06-27|2015-06-25|A cooling system for magnetic axial bearing|
    KR1020177002134A| KR102346384B1|2014-06-27|2015-06-25|A cooling system for magnetic axial bearing|
    US15/320,760| US10718382B2|2014-06-27|2015-06-25|Cooling system for axial magnetic bearing|
    BR112016030523-0A| BR112016030523B1|2014-06-27|2015-06-25|MAGNETIC BEARING SYSTEM AND COOLING METHOD OF A ROTATING WHEEL|
    AU2015279199A| AU2015279199B2|2014-06-27|2015-06-25|A cooling system for magnetic axial bearing|
    SA516380599A| SA516380599B1|2014-06-27|2016-12-25|A Cooling System for Magnetic Axial Bearing|
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