法国专利FR3038382A1 TOOLS FOR BALANCING A TURBOMACHINE MODULE

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专利摘要:
The invention relates to a tool for balancing a turbomachine module (10) in a balancer, this module comprising at least one stator casing (14) and a rotor (16) comprising a spindle shaft (18). longitudinal axis A and at least one blade stage (20) surrounded by said stator housing (14), said tooling comprising at least one balancing frame (14), comprising rotor guide bearings (16), first and second means (30, 32) configured to be attached to said stator housing (14), third and fourth means (34, 36) provided on said frame (24) for securing said first and second means (30, 32) frame, fifth means of transport of the frame (24), and sixth frame support means (84, 94) provided on said frame (24) and cooperating indifferently with the balancer and the fifth means of transport of the frame. frame (24).
公开号:FR3038382A1
申请号:FR1556220
申请日:2015-07-01
公开日:2017-01-06
发明作者:Alain Roland Luinaud；Alain Decocq；Francois Viviande
申请人:SNECMA SAS；
IPC主号:

专利说明:

The invention relates to a tool for balancing a turbomachine module. The invention relates more particularly to a tool for balancing a large or large-sized turbomachine module in a horizontal balancer, of the type used in the field of aeronautical powertrain for rotor balancing purposes. aeronautical turbomachines.
STATE OF THE PRIOR ART
A turbomachine comprises in known manner one or more rotors which are rotatably mounted in a stator.
A modern modern turbomachine is produced according to a modular design and as such comprises at least one rotor which consists of a plurality of elements manufactured separately and assembled mechanically. Similarly, the stator of such a turbomachine consists of a plurality of stator casings which are assembled to each other.
Thus, a turbomachine consists of an assembly of modules, at least some of which comprise at least one stator housing and an associated rotor which essentially comprises a rotor shaft having a longitudinal axis A and at least one blade stage. which is connected to a longitudinal end portion of said rotor shaft, and which is surrounded by said stator housing.
Conventionally, the balancing of such a turbomachine module is carried out directly in a balancer, that is to say that the constituent elements of said turbomachine module are mounted and supported directly in the balancer, without any interface whatsoever. it would be.
Thus, the stator housing is attached directly to a frame of the balancer, and the corresponding rotor is supported directly by bearings of the balancer.
This configuration gives overall satisfaction for small or medium size modules, but is not suitable for modules of large dimensions and masses for which the size and weight represent a constraint in terms of handling said module in said balancer.
Moreover, the elevation of the mass of the module associated with the tooling requires checking that the eigen modes of the assembly are outside the scope of use of the balancer.
It is furthermore not possible to manually move a high-size turbomachine module to install it in the balancer without risk of deterioration.
The functional clearances between the blade stage and the stator casing are substantially the same, whether the turbomachine module is a small or medium size module, or a high dimensional module.
Therefore, it is easily understood that manipulation of a high dimensional module, more likely to cause inappropriate movement of the rotor relative to the stator housing, could lead to inappropriate contacts between the blades of the d-stage. dawn and the stator housing, which could lead to deterioration of said stator housing and said blade stage.
It is therefore necessary to provide a tool for supporting a turbomachine module, its lifting, transport and installation in the balancer, this with the aid of a reduced number of interfaces for a secure transport of said module its removal and fixing in the balancer without risk of degradation.
Moreover, the balancing of a turbomachine module directly supported by the balancer involves making a number of adjustments during the installation of each module, which considerably increases the total duration of a balancing operation. . There is therefore a need for tooling to streamline balancing operations.
DESCRIPTION OF THE INVENTION The invention satisfies this need by proposing a tool for balancing a turbomachine module of the type described above, characterized in that said tooling comprises at least: a balancing frame, comprising bearings configured to receive and guide the shaft and the blade stage of the rotor, the position of at least one of said bearings being adjustable with respect to said frame, first and second means configured to be fixed to said stator housing, third and fourth means provided on said frame, for respectively fixing said first and second means to said frame, the position of at least one of said third and fourth means being adjustable with respect to said frame, fifth means of transport of the frame, - Sixth frame support means provided on said frame and configured to cooperate indifferently with the balancer and the fifth transport means of frame, for the support of said frame in said fifth transport means and in said balancer.
According to other features of the invention: the tooling comprises seventh removable means for locking the rotor relative to the stator housing, intended to immobilize the rotor relative to the stator housing during its transport to the balancer; said first means comprise an annular plate, which is configured to be fixed to a first end of the stator housing, which is intended to cooperate with the third means of the frame, and whose inner peripheral edge comprises the seventh removable means of locking the rotor said second means comprise a ring gear, which is configured to be fixed to a second opposite end of the stator casing, which is intended to cooperate with the third frame means, and which comprises means for adjusting the vertical and transverse position of the stator housing, - the balancing frame comprises at a first end near the stator housing u n first guide bearing with offset support, which comprises a tubular element whose first end, intended to be introduced into the stator housing, comprises at least one bearing receiving in rotation a support shaft received in the blade stage, and a second opposite end, intended to project out of the stator housing, comprises at least one peripheral surface which is clamped on a first support integral with the frame. the balancing frame comprises at a second end a second roller guide bearing which comprises a plate carrying two rollers on which the shaft is intended to roll, said plate being carried by a second support integral with the frame, and the position of said platen being adjustable transversely and vertically with respect to said second support, then permanently immobilized in a position adjusted by means of pins passing through the platen and said second support, and locked in said position by means of clamping screws arranged with clearance between the plate and the support, - the fifth transport means of the frame comprise a transport carriage adapted to carry the frame, - the first and second supports have a semi-cylindrical section and the transport carriage and the balancer comprise semi-cylindrical receiving surfaces, adjustable transversely and vertically and complementary of said first and second supports which form the sixth frame support means, and clamping means of said first and second supports in said receiving surfaces, - the tooling comprises eighth module lifting means, comprising slings intended for cooperate with the annular plate and with an end support of the rotor shaft and which are able to allow lifting of the module, and a removable intermediate support connecting the rotor shaft to the stator housing, - the tool comprises ninth lifting means of the frame having slings for cooperating with the annular plate and the second support, and which are capable of allowing the lifting of the frame, - the frame has an open trapezoid or U-shape and it comprises at least a horizontal branch adapted to rest on the carriage and two branches, in particular at least one vertical branch, whose ends bear the bearings of the frame, L'inv ention also relates to a calibration assembly for the adjustment of a tool of the type described above, characterized in that it comprises: - a standard stator housing, consisting of a stack of pigs of mass corresponding to that of the stator of the module, and which is intended to rest on the frame in a position corresponding substantially to the point of application of the weight of the stator housing of the module, and - a balanced standard rotor, moment of inertia and unbalance substantially corresponding to the rotor of the module to balance. The invention also relates to a method of adjusting before balancing a balancer and a tool using a calibration assembly of the type described above, which comprises: a first step of static adjustment of the balancer in which the semicylindrical bearing surfaces of the balancer are adjusted so that they are coaxial, - a second step during which a reference rotor and a standard stator housing are installed in the frame, - a third step, during which the frame equipped with the standard rotor and the stator stator housing is transferred to the semi-cylindrical bearing surfaces of the balancer, - a fourth stage of dynamic adjustment on the machine during which the vertical position is adjusted rollers relative to the platen of the second bearing, so that the bearing axes are parallel to an axis of a drive shaft of the balancer and then piercing the plate and the second sup port and inserted rods in the holes made to define the position of the plate, and finally locked the plate relative to the second support. Finally, the invention relates to a method for balancing a turbomachine module, characterized in that it comprises: a first step of lifting and putting in place, using the eighth lifting means, a module in a frame received in the fifth means of transport of a tool of the type described above, - a second step of transporting the module equipped with the frame to the balancer, using fifth means of transport, - a third step lifting and transferring the module equipped with the frame in the balancer using the ninth lifting means, and - a fourth balancing step of the module in the balancer.
PRESENTATION OF THE FIGURES The invention will be better understood and other objects, details, characteristics and advantages thereof will become more clearly apparent in the following detailed explanatory description of an embodiment of the invention given by way of example. of purely illustrative and non-limiting example with reference to the accompanying schematic drawings in which: - Figure 1 is a side view of a turbomachine module received in a balancing frame made according to the invention; FIG. 2 is a perspective view of the first means configured to be fixed to the stator housing; FIG. 3 is an axial view of the second means configured to be fixed to the stator casing; FIG. 4 is a perspective view showing the fifth means of transport of the frame receiving a frame; - Figure 5 is an axial sectional view of the first guide bearing offset from the module of the turbomachine; - Figures 6 and 7 are perspective views illustrating the mounting of an offset guide bearing in the module of the turbomachine; - Figure 8 is a perspective view illustrating a first step of lifting and placing, in a frame received in the fifth transport means, a turbomachine module with the eighth lifting means; - Figure 9 is a detailed perspective view illustrating the clamping of the first guide bearing offset in the frame; FIG. 10 is a detailed perspective view illustrating the reception of the rotor shaft in the second support and the reception of the second support in a reception range of the fifth transport means; - Figure 11 is a perspective view illustrating a third step of lifting and transferring the module equipped with its frame with the ninth lifting means; - Figure 12 is a side view illustrating the module equipped with the frame received in the bearings of the balancer; - Figure 13 is a perspective view showing the module equipped with the frame approaching the balancer; FIG. 14 is a perspective view illustrating the module equipped with the frame received in the balancer; FIG. 15 is an overall perspective view of a standard stator casing and a standard rotor for the calibration of a tool according to the invention; FIG. 16 is a perspective view showing the standard stator casing and the calibration rotor received in a frame according to the invention; FIG. 17 is a schematic view of a first step of static adjustment of a balancer for a balancing adjustment method according to the invention; FIGS. 18 and 19 are diagrammatic views showing the second stage of dynamic adjustment of a balancing adjustment method according to the invention.
DETAILED DESCRIPTION OF AN EMBODIMENT OF THE INVENTION
In the following description, like reference numerals designate like parts or having similar functions.
FIGS. 1 to 14 show a tool for balancing a turbomachine module 10 in a balancer 12. The balancer 12 has in particular been schematically represented in FIGS. 13 and 14.
In known manner, a turbomachine module 10 comprises at least one stator housing 14 and a rotor 16. The rotor 16 comprises a shaft 18 having a longitudinal axis of axis A and at least one blade stage 20 which is connected to a longitudinal end portion 22 of said rotor shaft 18 and which is surrounded by said stator housing 14.
This configuration has been shown in detail in FIGS. 1 and 8.
Conventionally, such a module 10 is received directly in the balancer 12, that is to say that the shaft 18 and the blade stage 20 are mounted in rotation directly in the balancer 12, and the housing of stator 14 is fixed directly to said balancer 12.
This configuration is generally satisfactory in the context of modules 10 of small or medium dimensions, but is particularly difficult to implement in the context of large modules 10 or large mass handling is problematic. The invention overcomes this drawback by proposing a tool allowing easy and reproducible installation of such a module 10 in a balancer 12. For this purpose, the tooling comprises at least one balancing frame 24 which is intended to to receive the module 10.
The balancing frame 24 comprises bearings 26 and 28 which are configured to receive and to respectively guide the shaft 18 and the blade stage 20 of the rotor 16.
According to the invention, the position of at least one of said bearings 26, 28 is adjustable relative to the frame 24 to allow adjustment of the rotor 10 relative to the balancer 12, as will be seen later in this description. The tooling further comprises first and second means 30, 32 which are configured to be fixed to the stator casing 14. The tooling also comprises third and fourth means 34, 36 which are provided on the frame 24 and which are intended to allow the fixing of the first means 30 and second means 32 to said frame 24.
Advantageously, the position of at least one of the third and fourth means 34, 36 is adjustable relative to said frame 24. The tool also comprises fifth frame conveying means 38 which are intended to allow the frame 24 to be conveyed to the balancer 12.
An essential characteristic of the invention is that the tooling advantageously comprises sixth means 40, 42 which are provided on the frame 24 and which are configured to cooperate indifferently with the balancer 12 and with the fifth means 38 for transporting the frame 24 in order to support said frame 24 in the fifth means 38 for transporting the frame or in the balancer 12 so as to allow easy transfer of the frame 24 of said fifth transport means 38 to said balancer 12.
The aforementioned means will now be described more explicitly.
According to the invention, the first means 30 comprise, as illustrated in FIG. 2, an annular plate 44 which is fixed at a first end 46 of the stator casing 14, as represented in FIG.
The annular plate 44 is intended to cooperate with the third means 34 of the frame. In the preferred embodiment of the invention, the frame 24 has an open trapezoidal shape and it comprises at least one horizontal leg 48 which is intended to rest on the fifth transport means 38 and comprises of parts and other of this branch 48 two branches, namely a vertical branch 50 and an inclined branch 52.
It will be understood that this configuration is not limiting of the invention and that the frame 24 could have another open shape, for example a U-shaped open shape having in the same way a horizontal branch 48 and two vertical branches.
The vertical leg 50 comprises a fixing lug 34 which constitutes the third means of the frame, on which is fixed the annular plate 44 constituting the first means fixed to the stator casing 14.
Furthermore, the annular plate 44 not only makes it possible to carry the stator casing 14, but also to clamp the rotor 16 with respect to the stator casing 14. For this purpose, an inner peripheral edge 54 of the annular plate comprises removable locking means of the rotor 16 relative to the stator housing 14, which are intended to immobilize the rotor 16 relative to the stator housing 14 during its transport to the balancer 12.
For example, these seventh removable locking means comprise eccentric nuts 56 which are angularly arranged in a regular manner around the inner peripheral edge 54 of the annular plate 44, as shown in FIG. 2, and which are intended to extend radially towards the outside. in contact with a bearing surface (not shown) of the blade stage 20 to immobilize said blade stage 20 inside the stator housing 14, and thereby to immobilize the rotor 16 by rotation compared to the stator housing 14.
The second means 32 which is configured to be fixed to the stator housing 14 comprises a ring gear 58 which, as illustrated in FIG. 1, is intended to be fixed to the stator casing 14 by a second end 60 of the stator casing 14 and which is intended to cooperate with the fourth means 36 provided on the frame 24.
In the preferred embodiment of the invention, the fourth means 36 consist of a tab 36 which is fixed on the inclined branch 52 of the frame 24, and which is fixed to a lower portion 60 of the ring 58 which has been shown in Figure 3, to allow this ring 58 to bear on the inclined arm 52 of the frame.
The second means 32 and fourth means 36 advantageously support the weight of the stator housing 14 which, in their absence, would be cantilevered, so as to keep it coaxial with the shaft 18 of the rotor 16 and thus avoid any interference between said stator housing 14 and the blade stage 20.
Advantageously, the fourth means consisting of the tab 36 can be adjusted relative to the lower portion 60 of the ring 58 so as to allow adjustment in the vertical direction of said ring 58. This configuration makes it possible to adjust the coaxiality of the casing 14 and of the rotor 16.
This configuration makes it possible to prevent the casing 14 from being cantilevered with respect to the vertical arm 50 of the frame 24, and that its weight tends to misalign it with the rotor 16.
Note that, in known manner, the annular plate 44 as the ring 58 can be fixed to the stator housing 14 by means of screws and nuts. For example, fixing nuts 64 are arranged around the periphery of the annular plate 44 in FIG.
Furthermore, the bracket 36 of the inclined arm 52 of the frame 24 has holes which are intended to be arranged opposite holes 66 of the lower part of the ring 58. These holes are intended to be traversed with clearance by screws 62 so as to allow relative movement of the ring 58 relative to the tab 36 and then to allow its locking. Thus the screws 62 constitute a means of simple adjustment of the vertical and transverse position of the stator casing 14, which makes it possible to guarantee the coaxiality of said stator casing 14 with the rotor 16.
To ensure the rotational guidance of the rotor 16 in the frame 24, the balancing frame 24 comprises at a first end which is arranged near the casing 14 of the stator, that is to say at the end of the vertical arm 50, a first guide bearing with offset support 28.
The offset bearing guide bearing 28, also known technically as the "false bearing", essentially comprises, as illustrated in FIGS. 5 to 7, a tubular element 68 which has a first end 70 which is intended to to be introduced, as shown in Figure 7, in the casing 14 of the stator. This end 70 comprises at least one bearing 72 receiving in rotation the blade stage 20.
More particularly, the blade stage 20 comprises an end bearing 74 which is rotatably mounted inside the bearing 72 of the tubular element 70, but also via a bearing 76 which is mounted around a support shaft 78 which is received inside the casing 14 inside the vane stage 20 and whose end 80 projecting out of the casing 14 is received in the element This assembly makes it possible to ensure a guide in rotation of the blade stage 20 radially between the support shaft 78 and the tubular element 68.
A second end 82 of the tubular element 68 is intended to project out of the stator casing 14 and has a peripheral bearing which, as shown in FIG. 9, is clamped on a first support 84 secured to the frame 24. Peripheral bearing is offset axially from the bearing 76, since it bears on the outside of the stator casing 14.
For mounting the offset guide bearing 28, the support shaft 78 is first introduced into the bearing 76 of the vane stage 20, as shown in FIG. 6, and then the support shaft is introduced. in the tubular element 68 which is slid into the stator housing 84 by means of a guide ramp 69, as shown in FIG. 7. The tubular element 68 can then be fixed to the frame 24.
More particularly, as illustrated in FIG. 9, the first support 84 secured to the frame 24, which receives the peripheral surface 82 of the tubular element 68, has a semi-cylindrical section and has an outer periphery 42 which forms the sixth means. frame supports which are configured to cooperate indifferently with the balancer 12 or with the transport means 38. For this purpose, the transport means 38 and the balancer 12 comprise receiving surfaces 88 of the first support 84, complementary to the outer periphery 42 of the support 84, as shown in FIGS. 11 and 13.
The transport means 38 and the balancer 12 also comprise clamping means 85 of the first support 84 so as to allow it to be immobilized relative to the transport means 38 or to the balancer 12. For example, in FIG. the clamping means 85 of the transport means 38 comprises a transversely tilting locking lever.
It will be understood, however, that any known means of the state of the art may be suitable for the proper implementation of these clamping means. At a second end of the balancing frame 24, which corresponds to the end of its inclined branch 52, the balancing frame 24 comprises a second roller guide bearing 26 which comprises, as illustrated in FIG. platinum 90 carrying two rollers 92 on which the shaft 18 is intended to roll.
The plate 90 is carried by a second support 94 which is integral with the frame 24. Clamping screws 98 are arranged with clearance between the plate 90 and the second support 94 so as to allow a latitude of adjustment of the plate 90 relative to the second support 94.
The screws 98 being loosened, the position of the plate 90 is capable of being previously set transversely and vertically with respect to said second support 94, then to be permanently immobilized in a position adjusted with respect to the second support 94. The plate 90, once set on the second support 94, is pierced at the same time as the second support 94, and locked in this position by means of pins 96 which are received in the holes thus passing through the plate 90 and the second support 94. Then the plate 90 is locked in said position by means of the clamping screws 98.
This defines the position of the axis of the shaft 18 relative to the second support 94.
Advantageously, an adjustment system by wheel and worm 100 can be arranged between the second support 94 and the plate 90 to adjust vertically the position of the plate 90 relative to the second support 94. The shaft 18 can be maintained in contact rollers 92 of the plate 90 by means of a transverse flange 102 which is fixed at its opposite ends to the support 94 and which comprises a central roller whose axle 104 is seen in Figure 10. The roller rolls on the 18 and thus allows to maintain the shaft 8 in contact with the rollers 92.
As will be seen in the following description, the possibility of vertical adjustment of the second bearing 28 ensures the parallelism of the axis A of the rotor 16 with a B axis of the balancer so as to prevent the floor blade 20 does not present an unbalance because of its inclination.
In the same manner as before, the second support 94 has a semi-cylindrical section including a cylindrical surface 40 which is intended to be received in complementary semi-cylindrical receiving surfaces 89 of the transport means 38 and the balancer 12.
In the same way as for the first support 84, clamping means, such as a lever 95 shown in FIG. 8, make it possible to immobilize the second support in said reception surfaces 89.
As illustrated in FIG. 4, the fifth means 38 for transporting the frame preferably consist of a transport carriage 38 able to carry the frame 24.
For the most part, this carriage 38 comprises two transverse beams 106 provided at their transverse ends with rollers 108, and between which is arranged a structure 110 on which the horizontal branch 48 of the frame 24 is capable of resting.
For example, this structure 110 comprises a central beam 112 which has two vertical tabs 114 intended to laterally immobilize the horizontal branch 48 of the frame 24.
The carriage 38 comprises two vertical brackets 116 at the end of which are arranged the semi-cylindrical receiving surfaces 40, 42.
To allow the installation of the module 16 in the frame 24, the tooling comprises eighth lifting means of the module 16.
These means comprise slings 120 which are intended to cooperate with the annular plate 44. For this purpose, the annular plate 44 comprises two diametrically opposed horizontal arms 122, the ends of which are shaped in bearings 124 which are capable of being received in rings. 125 arranged at the end of the slings 120.
In addition, the eighth lifting means of the module 10 comprises a sling 121 and a support 131 intended to support the end of the shaft 18 of the rotor 16.
The eighth lifting means also comprise, as shown in FIG. 8, a removable intermediate support 128 linking the rotor shaft 16 to the stator casing, said removable intermediate support 128 comprising, for example, a plate which is fixed in its seat. upper part to the stator housing 14 by means of screws 126, and below which extends a clamp 130 enclosing the shaft 18.
As illustrated in FIG. 8, the eighth lifting means make it possible to support the rotor 16 and the stator casing 14 in order to place them in the frame 24. The support 128 can be disassembled after the stator casing 14 has been fixed 24. The tooling also includes ninth lifting means of the frame 24 which are intended to allow the lifting of the frame 24 once it is equipped with the rotor 16.
As illustrated in FIG. 11, these ninth lifting means comprise slings 120 whose rings 125 are intended to cooperate with the diametrically opposite horizontal arms 124 of the support, but also slings 132 intended to be fixed to the second support 94 to allow the lifting of the frame 24 by the end of its inclined branch 52. The set of previously described tooling allows to balance a turbomachine module 16 according to a repetitively reproducible process for rotors 16 successive.
The frame 24, which rests on said carriage via its horizontal branch 48, its vertical branch 50, and its inclined branch 52, which rest respectively on the semicylindrical bearing surfaces 88 and 89 respectively, is installed in the carriage 38. brackets 118 and 116 of the carriage 38.
The method comprises a first step of lifting and placing, using the eighth lifting means, as shown in Figure 8, a module 10 in a frame 24. Once installed, the rotor is flanged 16 relative to the frame 44 of the housing 14 by means of the eccentric nuts 56.
Then, during a second transport step of the module equipped with its frame 24, said module 10 equipped with its frame 24 is conveyed to the balancer 12 by means of the carriage 38, so as to place the carriage 38 at immediate proximity of the balancer 12.
It then follows a third step of lifting and transferring the module 10, equipped with the frame 24, in the balancer 12 using the ninth previously described lifting means.
In this case, the entire module 10 and the frame 24 are transferred to the balancer 12.
In the same manner as before, the frame then rests on the semi-cylindrical bearing surfaces 88 and 89 of the balancer 12. It is then possible to unclamp the rotor 16.
Finally, the method comprises a fourth balancing step of the module 10 in the balancer 12.
It should be noted that such balancing is possible only provided that the axis A of the rotor 16 is, on the one hand, coaxial with the bearings 26 and 28 of the frame 24 and, on the other hand, that the A axis of the rotor 16 is parallel to the axis B of the balancer 12, otherwise the inclination of the module 10 will cause the appearance of an unbalance that will distort the reading of the balancer.
It is therefore necessary to adjust the frame 24 and the balancer 12 prior to the balancing operations.
Indeed, the frame 24 being an open structure, the mass of the module 10 tends to open this structure and in particular to separate from each other the vertical leg 50 and the inclined branch 52, so that the initial coaxiality of the bearings 26, 28 is modified by the implantation of the module 10 in the frame 24.
To overcome this drawback, the invention proposes a calibration assembly 10 'for adjusting the tooling.
This calibration assembly comprises, as illustrated in FIG. 15, a standard stator casing 14 'which consists of a stack of pigs 134 of mass equivalent to that of the stator casing 14 to be balanced and which is intended for be positioned, as shown in Figure 16, at the point of application of the weight of the stator housing 14 of the actual module 10. The calibration assembly also comprises a balanced standard rotor 16 ', which has been shown in FIG. 15 in a storage position on a support 136 intended to allow its storage when it is not in use. This standard rotor 16 'has a moment of inertia and an imbalance corresponding to the rotor 16 of the module to be balanced.
To calibrate the frame 24, the procedure is as follows.
A first step of static adjustment of the balancer is first carried out during which the coaxiality of the semi-cylindrical bearing surfaces 88, 89 of the balancer is adjusted so that they are coaxial as shown in FIG. FIG. 17. The axes A88 and A89 of the semi-cylindrical bearing surfaces are thus adjusted so that they form no more than one axis A.
In this way, the balancer is adapted to receive the first and second supports 84, 94 of the frame 24 in a coaxial configuration corresponding to the actual configuration of the rotor 16 to be balanced.
Any means known in the art can be used for the verification of this coaxiality.
Then, as illustrated in FIG. 16, there is, in the frame 24, the standard stator casing 14 'and the reference rotor 16' so as to cause the branch 50 and the branch 52 of the frame 24 to move apart, the frame then being in a load configuration corresponding to that of the balancing.
Then, during a third step, the frame 24 equipped with the standard rotor 16 'and the standard stator casing 14' is transferred to the semi-cylindrical bearing surfaces 88, 89 of the balancer 12.
The adjustment made during the first step of static adjustment of the balancer ensures that the semi-cylindrical surfaces of the balancer 12 accommodate the supports 84, 94 of the frame 24 in a satisfactory alignment.
It is then necessary to perform a fourth dynamic adjustment step on the balancer during which the vertical position of the rollers 92 of the plate 90 is adjusted by adjusting the position of the plate 90 relative to the second support 94, way to move from an uncontrolled inclination position of the axis A of the rotor 16 ', as shown in Figure 18 in which the axis A of the rotor 16' forms an undetermined angle with the axis B of the 12, at a set position in which the axis A of the standard rotor 16 'is parallel to the axis B of the balancer. The parallelism of these axes A, B makes it possible to prevent the rotor 16 from presenting an imbalance detrimental to a satisfactory measurement.
It is then advisable to keep this adjustment by piercing the plate 90 and the support 94 and by inserting the rods 96 so as to maintain this position, then tightening the screws 98 so as to definitively immobilize the plate 90 relative to the second support 94.
It is therefore possible to remove from the balancer 12 the frame 24 which is now set in a final position. The standard rotor 16 'and the calibration casing 14' of the frame 24 are then disassembled, the frame 24 then being ready to receive a real module 10 comprising a rotor 16 and a stator casing 14 for its equilibration.
Advantageously, the frame 24 and the balancer 12 being adjusted once and for all for the rotors 16 of the same type, this configuration offers a significant time saving in the context of the balancing of a series of identical rotors 16 because the settings allow the reproducibility of the balancing operation without intermediate adjustment.

权利要求:
Claims (14)
[1" id="c-fr-0001]
1. Tooling for balancing a turbomachine module (10) in a balancer (12), this module comprising at least one stator housing (14) and a rotor (16) having a shaft (18) of axis longitudinal member A and at least one blade stage (20) which is connected to a longitudinal end portion (22) of said shaft (18) and which is surrounded by said stator housing (14), said tool comprising at least: a balancing frame (14) comprising configured bearings (26, 28) for receiving and guiding the shaft (18) and the blade stage (20) of the rotor (16), the position of at least one of said bearings (28) being adjustable with respect to said frame (24), - first and second means (30,32) configured to be fixed to said stator housing (14), - third and fourth means (34,36). ) provided on said frame (24), for respectively fixing said first and second means (30, 32) to said frame, the position of at least one of said third and fourth means s (34, 36) being adjustable with respect to said frame, - fifth means (38) for transporting the frame (24), - sixth frame support means (84, 94) provided on said frame (24) and configured to cooperate indifferently with the balancer (12) and with the fifth transport means (38) of the frame (24), for the support of said frame (24) in said fifth transport means (38) and in said balancer ( 12).
[2" id="c-fr-0002]
2. Tooling according to the preceding claim, characterized in that it comprises seventh removable means (56) for locking the rotor (16) relative to the stator housing (14), intended to immobilize the rotor (16) relative to the stator housing (14) during transport to the balancer (16).
[3" id="c-fr-0003]
3. Tooling according to the preceding claim, characterized in that said first means comprise an annular plate (44), which is configured to be fixed to a first end (46) of the stator casing (14), which is intended to cooperate with the third means (34) of the frame (24), and whose inner peripheral edge (54) comprises the seventh removable means (56) for locking the rotor (16).
[4" id="c-fr-0004]
4. Tooling according to the preceding claim, characterized in that said second means (32) comprise a ring gear (58), which is configured to be fixed to a second opposite end (60) of the stator casing (14), which is intended to cooperate with the third means (36) of the frame (24), and which comprises means for adjusting the vertical and transverse position of the stator housing (14).
[5" id="c-fr-0005]
Tooling according to one of claims 1 to 4, characterized in that the balancing frame (24) has at a first end, in the vicinity of the stator casing (14), a first offset bearing guide bearing ( 28), which comprises a tubular element (68) whose first end (70) intended to be introduced into the stator housing (14) comprises at least one bearing (72) receiving in rotation a support shaft (78) received in the blade stage (20), and a second opposite end (82) for projecting out of the stator housing (14), has at least one peripheral bearing (42) which is clamped on a first support (84) secured to the frame (24).
[6" id="c-fr-0006]
6. Tooling according to the preceding claim, characterized in that the balancing frame (24) comprises at a second end a second roller guide bearing (26) which comprises a plate (90) carrying two rollers (92). ) on which the shaft (18) is intended to roll, said plate being carried by a second support (94) integral with the frame (24), and the position of said plate (90) being adjustable transversely and vertically relative to said second support (94), then permanently immobilized in a position adjusted by means of pins (96) passing through the plate (90) and said second support (94), and locked in said position by means of screws clamping means (98) arranged with clearance between the plate (90) and the support (94).
[7" id="c-fr-0007]
7. Tooling according to one of the preceding claims, characterized in that the fifth transport means (38) of the frame (24) comprise a transport carriage (38) adapted to carry the frame (24).
[8" id="c-fr-0008]
8. Tooling according to the preceding claim taken in combination with claims 5 and 6, characterized in that the first and second supports (84, 94) have a semi-cylindrical section and in that the carriage (38) and the balancer (12) have transversely and vertically adjustable semi-cylindrical receiving surfaces (88, 89) complementary to said first and second supports (84, 94), and means for clamping said first and second supports (84, 94). ) which form the sixth frame support means in said receiving lands (88, 89).
[9" id="c-fr-0009]
9. Tooling according to one of claims 3 to 8, characterized in that it comprises eighth module lifting means, comprising slings (120, 121) for cooperating with the annular plate (44) and with a support at the end (131) of the shaft (18) of the rotor (16) and which are adapted to allow lifting of the module (10), and a removable intermediate support (128) connecting the rotor shaft (18) ( 16) to the stator housing (14).
[10" id="c-fr-0010]
10. Tooling according to claims 3 and 6 taken in combination, characterized in that it comprises ninth lifting frame means having slings (120, 132) for cooperating with the annular plate (44) and with the second support (94), and which are adapted to allow the lifting of the frame (24).
[11" id="c-fr-0011]
11. Tooling according to claim 7 or 8, characterized in that the frame (24) has an open trapezoidal or U-shaped shape and that it comprises at least one horizontal branch (48) adapted to rest on the carriage ( 38) and two branches (50, 52), in particular at least one vertical branch (50), the ends of which bear the bearings (26, 28) of the frame (24).
[12" id="c-fr-0012]
12. Calibration assembly (10 ') for adjusting a tool according to the preceding claim, characterized in that it comprises: - a standard stator casing (14') consisting of a stack of pigs (134); ) of mass corresponding to that of the stator (14) of the module (10), and which is intended to rest on the frame (24) in a position corresponding substantially to the point of application of the weight of the stator casing (14) of the module (10), and - a balanced standard rotor (16 '), moment of inertia and unbalance substantially corresponding to the rotor of the module (16) to be balanced.
[13" id="c-fr-0013]
13. A method of adjusting before balancing a balancer (12) and a tool according to claim 11 with the aid of a calibration assembly (10 ') according to claim 12, characterized in that it comprises a first step of static adjustment of the balancer (12), during which the semicylindrical bearing surfaces (88, 89) of the balancer are adjusted so that they are coaxial, - a second step during of which a reference rotor (16 ') and a standard stator housing (14') are installed in the frame (24), - a third step, during which the frame (24) equipped with the reference rotor (16) is transferred. ') and the standard stator housing (14') on the semi-cylindrical bearing surfaces of the balancer, - a fourth dynamic adjustment step on the balancer during which the vertical position of the rollers (92) is adjusted by adjusting the plate (90) relative to the second support (94), so that the bearing axes A are to a B-axis of a drive shaft of the balancer (12), then the plate (90) and the second support (94) are drilled and pins (96) are inserted into the holes made in order to define the position of the plate (90), and finally the plate (90) is locked with respect to the second support (94),
[14" id="c-fr-0014]
14. A method of balancing a turbomachine module (10), characterized in that it comprises: a first step of lifting and putting in place, using the eighth lifting means, a module; (10) in a frame (24) received in the fifth transport means (38) of a tool according to claims 1 to 11, - a second transport step of the module (38) equipped with the frame (24) to the balancer (12), using the fifth transport means (35), - a third step of lifting and transferring the module (10) equipped with the frame (24) in the balancer (12) using the ninth lifting means, and - a fourth balancing step of the module (10) in the balancer (12).

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同族专利:

公开号 | 公开日

US20180172111A1|2018-06-21|

EP3317631A1|2018-05-09|

FR3038382B1|2017-07-07|

US10190655B2|2019-01-29|

EP3317631B1|2019-06-12|

RU2711248C2|2020-01-15|

CN107735662B|2020-05-22|

RU2017142110A|2019-08-01|

CA2987841A1|2017-01-05|

RU2017142110A3|2019-10-22|

CN107735662A|2018-02-23|

BR112017025958A2|2018-08-14|

WO2017001745A1|2017-01-05|

引用文献:

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US3146623A|1958-03-17|1964-09-01|American Mach & Foundry|Spin-test and balancing machine|

US4586225A|1983-04-15|1986-05-06|Societe Nationale D'etude Et De Construction De Moteurs D'aviation S.N.E.C.M.A.|Apparatus for the transfer of a complete turbine module from a balancing machine to an engine and vice versa, and method for operating the said apparatus|

SE387408B|1974-12-23|1976-09-06|Stal Laval Turbin Ab|PROCEDURE FOR INSTALLATION IN A MACHINE HALL OF A GAS TURBINE UNIT|

US4157613A|1977-12-23|1979-06-12|D. A. Griffin Corp.|Apparatus for inserting a rotor into a stator|

US4451979A|1980-10-27|1984-06-05|Elliott Turbomachinery Company, Inc.|Assembly and disassembly apparatus for use with a rotary machine|

FR2499652B1|1981-02-11|1985-03-22|Snecma|

US4567649A|1983-05-04|1986-02-04|General Electric Company|System for heating, disassembly, handling and reassembly of a turbine rotor|

RU2059214C1|1992-05-18|1996-04-27|Николай Петрович Дядченко|Method and device for determination of unbalance of rotor|

US6341419B1|2000-02-29|2002-01-29|General Electric Company|Loop stacked rotor assembly|

US8672606B2|2006-06-30|2014-03-18|Solar Turbines Inc.|Gas turbine engine and system for servicing a gas turbine engine|

FR2911959B1|2007-01-29|2009-04-24|Snecma Sa|METHOD FOR MODULAR TURBOMACHINE ROTOR BALANCING|

CN102564697B|2010-12-24|2014-07-23|沈阳黎明航空发动机有限责任公司|Dynamic balance assembly testing device of engine rotors|

KR102191182B1|2013-03-28|2020-12-16|에이비비 스위츠랜드 엘티디.|Cantilever slide for installing and removing a rotor block|FR3076236B1|2017-12-28|2019-12-06|Safran Aircraft Engines|TOOL FOR DISASSEMBLING AN ANNULAR PART OF A TURBOMACHINE, METHOD FOR DISASSEMBLY AND ASSEMBLY THEREOF|

FR3087686B1|2018-10-31|2020-12-11|Safran Aircraft Engines|TOOLS FOR BALANCING A TURBOMACHINE MODULE INCLUDING AN OVERHEAD STATOR|

CN110469366B|2019-07-31|2022-03-04|中国航发沈阳发动机研究所|Device for balancing stator of low-pressure turbine|

法律状态:
2016-07-18| PLFP| Fee payment|Year of fee payment: 2 |

2017-01-06| PLSC| Search report ready|Effective date: 20170106 |

2017-04-28| PLFP| Fee payment|Year of fee payment: 3 |

2018-06-21| PLFP| Fee payment|Year of fee payment: 4 |

2018-09-14| CD| Change of name or company name|Owner name: SAFRAN AIRCRAFT ENGINES, FR Effective date: 20180809 |

2019-06-21| PLFP| Fee payment|Year of fee payment: 5 |

2020-06-23| PLFP| Fee payment|Year of fee payment: 6 |

2021-06-23| PLFP| Fee payment|Year of fee payment: 7 |

优先权:

申请号 | 申请日 | 专利标题

FR1556220A|FR3038382B1|2015-07-01|2015-07-01|TOOLS FOR BALANCING A TURBOMACHINE MODULE|FR1556220A| FR3038382B1|2015-07-01|2015-07-01|TOOLS FOR BALANCING A TURBOMACHINE MODULE|

EP16739233.1A| EP3317631B1|2015-07-01|2016-06-21|Tool for balancing a turbine engine module|

PCT/FR2016/051513| WO2017001745A1|2015-07-01|2016-06-21|Tool for balancing a turbine engine module|

BR112017025958-3A| BR112017025958A2|2015-07-01|2016-06-21|tool for balancing a turbomachine module|

CA2987841A| CA2987841A1|2015-07-01|2016-06-21|Tool for balancing a turbine engine module|

CN201680038690.7A| CN107735662B|2015-07-01|2016-06-21|Tool for balancing a turbine engine module|

US15/738,091| US10190655B2|2015-07-01|2016-06-21|Tool for balancing a turbine engine module|

RU2017142110A| RU2711248C2|2015-07-01|2016-06-21|Tool for gas turbine engine module balancing|

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