Low-pressure turbine rotor balancing device, balancing test method and special bearing machining method of low-pressure turbine rotor balancing device

Abstract

The invention discloses a low-pressure turbine rotor balancing device, a balancing test method and a special bearing machining method thereof.The balancing device comprises a first positioning and clamping component and a second positioning and clamping component, the special bearing inner ring comprises an inner hole matched with a low-pressure turbine rotor shaft neck, an inner hole step face matched with the axial end face of the low-pressure turbine rotor shaft neck, a surface raceway matched with balls of the self-aligning ball bearing standard component and a cylindrical surface located on the outer side of the inner hole of the first bearing seat and used for adjusting the unbalance amount of the special bearing inner ring. When a balance test is carried out, axial and radial positioning is carried out through matching of the outer circular surface of a low-pressure turbine rotor journal and an inner hole of a special bearing inner ring, positioning of the axial end surface of the journal and an inner hole step surface of the special bearing inner ring, axial locking of double nuts, and matching of a second positioning and clamping part and a low-pressure turbine rotor bearing inner hole. The device meets the clamping and fixing requirements of the low-pressure turbine rotor balance test, and is low in cost and easy to implement.

Description

Technical Field

[0001] The invention belongs to the technical field of aviation engine parts manufacturing, in particular to a low-pressure turbine rotor balancing device, a balancing test method and a special bearing processing method thereof. Background Art

[0002] The low-pressure turbine rotor is an important part in aircraft engines, and the balance test is one of the key tests for such parts in aircraft engines. Figure 1 As shown in the figure, the double-dotted line draws the outline of the low-pressure turbine rotor. During the balancing test, the bearing is one of the key parts in the balancing device. However, the standard bearing parts purchased on the market cannot meet the clamping and positioning requirements of the low-pressure turbine rotor. Special bearing parts need to be designed, manufactured and replaced to meet the use requirements. Summary of the invention

[0003] The present invention aims to provide a low-pressure turbine rotor balancing device, a balancing test method and a special bearing processing method thereof, wherein the balancing device needs to be designed according to the low-pressure turbine rotor and the balancing machine, and is used to clamp the shaft neck, position the axial direction of the low-pressure turbine rotor, and be fixed on the balancing machine for a balancing test, thereby meeting the requirements of the low-pressure turbine rotor balancing test. Furthermore, the processing and manufacturing cost of the special bearing is relatively low, the processing method is relatively simple, and there is no need to customize it through a bearing manufacturer.

[0004] To achieve the above object, the present invention adopts the following technical solutions:

[0005] A low-pressure turbine rotor balancing device comprises a first positioning and clamping component connected to a low-pressure turbine rotor journal, and a second positioning and clamping component connected to an inner hole of a low-pressure turbine rotor bearing, wherein:

[0006] The first positioning and clamping component comprises a first bearing seat, a mounting groove for positioning with a balancing machine is provided on the circumferential surface of the first bearing seat, a self-aligning ball bearing standard part without an inner ring is installed in the inner hole of the first bearing seat, the inner ring position of the self-aligning ball bearing standard part is replaced with a special bearing inner ring, and the axial end face of the first bearing seat is connected to a bearing pressing ring for pressing the self-aligning ball bearing standard part;

[0007] The inner ring of the special bearing comprises an inner hole matched with the shaft neck of the low-pressure turbine rotor, an inner hole step surface matched with the axial end face of the shaft neck of the low-pressure turbine rotor, a surface raceway matched with the balls of the self-aligning ball bearing standard part, and a cylindrical surface located outside the inner hole of the first bearing seat and used to adjust the unbalance amount of the inner ring of the special bearing;

[0008] The second positioning and clamping component includes a second bearing seat, a circumferential surface of the second bearing seat is provided with a mounting groove for positioning with the balancing machine, a bearing seat spindle is installed in the inner hole of the second bearing seat and is plugged into the inner hole of the low-pressure turbine rotor bearing, a bearing seat sleeve is installed at the end of the bearing seat spindle, and the end of the bearing seat spindle is matched with the inner hole of the low-pressure turbine rotor bearing through the bearing seat sleeve.

[0009] Furthermore, the low-pressure turbine rotor balancing device also includes: a first clamping nut and a second clamping nut, wherein the first clamping nut and the second clamping nut are connected to the external thread of the shaft surface on one side of the low-pressure turbine rotor shaft neck, and the first clamping nut or the second clamping nut is clamped on the end face of the inner ring of the special bearing located on the outside of the first bearing seat.

[0010] Furthermore, the low-pressure turbine rotor balancing device further comprises a special hexagonal bolt, which penetrates the second bearing seat and points to the low-pressure turbine rotor bearing. The special hexagonal bolt is used to disassemble the bearing seat spindle, and the low-pressure turbine rotor bearing is tightened by rotating the special hexagonal bolt, thereby separating the bearing seat spindle from the inner hole of the low-pressure turbine rotor bearing.

[0011] A method for processing the inner ring of the aforementioned special bearing comprises the following steps:

[0012] Step 1: disassemble the standard parts of the self-aligning ball bearing, remove the inner ring, and keep the balls, ball cages and outer rings;

[0013] Step 2, obtaining various parameters of the self-aligning ball bearing standard parts in step 1, including ball diameter Φd, inner ring bearing raceway center distance C, inner ring outer diameter ΦD1, inner ring raceway R value, bearing nominal width B and outer ring raceway diameter ΦM value;

[0014] Step 3: Calculate the outer diameter ΦD2 of the inner ring raceway of the special bearing based on the parameters of the self-aligning ball bearing standard parts obtained in step 2;

[0015] Step 4: Processing the inner ring of the special bearing according to the outer diameter Φd2 of the low-pressure turbine rotor journal, the outer diameter ΦD2 of the inner ring raceway of the special bearing, the center distance C of the inner ring bearing raceway, the ball diameter Φd and the nominal width B of the bearing;

[0016] Step 5, performing a dynamic balancing test on the inner ring of the special bearing obtained by processing, and obtaining an unbalance amount that meets the requirements by removing the material on the cylindrical surface of the inner ring of the special bearing used for adjusting the unbalance amount;

[0017] Step six, assemble the special bearing inner ring that meets the unbalance requirement in step five as the bearing inner ring with the balls, ball cage and outer ring of the self-aligning ball bearing standard parts in step one.

[0018] As an option, in step three, the calculated outer diameter ΦD2 of the inner ring raceway of the special bearing minus an active amount is used to obtain the final value of the outer diameter ΦD2 of the inner ring raceway of the special bearing processed in step four.

[0019] As an option, in step 4, the processing steps of the inner ring of the special bearing include:

[0020] Step 1: Use bar stock to turn all surfaces and leave a single-side allowance. All surfaces include the end face, inner hole and outer cylindrical surface of the inner ring of the special bearing;

[0021] Step 2: Grind two end faces of the axial length of the inner ring of the special bearing using a grinder;

[0022] Step 3: remove burrs and round off sharp edges;

[0023] Step 4: quenching and tempering;

[0024] Step 5: Grind the two end faces of the axial length of the inner ring of the special bearing again, leaving a single-side margin;

[0025] Step 6: Finely grind each surface of the inner hole of the inner ring of the special bearing and the corresponding end surface, leaving a single-side margin on each surface;

[0026] Step seven, artificial aging;

[0027] Step 8: Grind the two end faces of the axial length of the inner ring of the special bearing again, leaving a single-side margin;

[0028] Step nine, bluing;

[0029] Step 10, grinding the two end faces of the axial length of the inner ring of the special bearing again;

[0030] Step 11, fine grinding each surface of the inner hole of the inner ring of the special bearing and the corresponding end surface;

[0031] Step 12, grinding the outer circumferential surfaces and corresponding end surfaces of the inner ring of the special bearing;

[0032] Step 13: Balance test: remove the material on the cylindrical surface of the inner ring of the special bearing used to adjust the imbalance to obtain an imbalance that meets the requirements.

[0033] The low-pressure turbine rotor balancing test method adopts the above-mentioned balancing device and comprises:

[0034] Through the cooperation between the outer cylindrical surface of the low-pressure turbine rotor shaft neck and the inner hole of the inner ring of the special bearing, the axial end face of the shaft neck and the inner hole step surface of the inner ring of the special bearing are positioned, and the low-pressure turbine rotor is axially locked through the first clamping nut, the second clamping nut, the shaft surface external thread on one side of the low-pressure turbine rotor shaft neck and the end face of the inner ring of the special bearing, and is positioned, clamped and fixed with the balancing machine through the mounting groove on the first bearing seat;

[0035] Axial and radial positioning is performed by the cooperation between the bearing seat bushing and the inner hole of the low-pressure turbine rotor bearing, and the positioning, clamping and fixing are performed on the balancing machine through the mounting groove on the second bearing seat.

[0036] Compared with the prior art, the present invention provides a low-pressure turbine rotor balancing device, and at the same time provides a calculation and processing method for the inner ring of a special bearing in the balancing device. The low-pressure turbine rotor balancing device processed by this method is used for the balancing test of the low-pressure turbine rotor. After inspection and delivery to the site for use and verification, all parameters ensure the balancing test requirements of the low-pressure turbine rotor. On the other hand, the special bearing processing method of the present invention is low-cost, easy to implement, and does not require customized production by bearing manufacturers. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] Figure 1 It is a schematic diagram of the balancing device;

[0038] Figure 2 for Figure 1 Schematic diagram of the special bearing at the middle left end;

[0039] Figure 3 for Figure 2 Schematic diagram of inner ring of special bearing;

[0040] Figure 4 This is a schematic diagram of standard parts of a self-aligning ball bearing;

[0041] Figure 5 It is a drawing for calculation of inner ring of special bearing;

[0042] In the figure: 1-second bearing seat, 2-bearing seat spindle, 3-bearing seat bushing, 4-first bearing seat, 5-special bearing inner ring, 6-bearing pressure ring, 7-first clamping nut, 8-second clamping nut, 9-self-aligning ball bearing standard part, 10-hexagon head bolt, 11-slotted countersunk screw, 12-special hexagon bolt. DETAILED DESCRIPTION

[0043] The present invention is further described below in conjunction with specific embodiments, but it should not be understood that the scope of the subject matter described in the present invention is limited to the following embodiments. Without departing from the above-mentioned technical ideas of the present invention, various modifications, substitutions and changes made according to common technical knowledge and customary means in the field are included in the scope of the present invention.

[0044] like Figure 1As shown, the low-pressure turbine rotor balancing device includes two parts, one of which is a left-end positioning and clamping component of the balancing device composed of a first bearing seat 4, a special bearing inner ring 5, a bearing pressure ring 6, a first clamping nut 7, a second clamping nut 8, a self-aligning ball bearing standard part 9, and a hexagonal bolt 10. The other part is a right-end positioning and clamping component of the balancing device composed of a second bearing seat 1, a bearing seat spindle 2, a bearing seat bushing 3, a slotted countersunk screw 11, and a special hexagonal bolt 12. The hexagonal bolt 10 is used to fix the bearing pressure ring 6 on the end face of the first bearing seat 4 so as to clamp the self-aligning ball bearing standard part 9 and the special bearing inner ring 5. The slotted countersunk screw 11 is used to connect the bearing seat bushing 3 and the bearing seat spindle 2. The special hexagonal bolt 12 is evenly distributed on the second bearing seat 1, and the bearing seat spindle 2 is pushed out from the inner hole of the low-pressure turbine rotor bearing through the thread. The bearing seat spindle 2 is axially limited with the second bearing seat 1 through the step surface at the end.

[0045] Figure 2 The special bearing assembled with the self-aligning ball bearing standard part 9 and the special bearing inner ring 5 is shown. The processing method of the special bearing is as follows:

[0046] Buy Figure 4 The self-aligning ball bearing standard part 9 shown: cylindrical bore self-aligning ball bearing, type 1318, in accordance with standard GB / T281-1994;

[0047] Disassembly Figure 4 The self-aligning ball bearing standard parts 9 shown are arranged according to the categories of balls, inner rings, outer rings and ball cages;

[0048] Measurement Figure 4 The ball diameter Φd, inner ring bearing raceway center distance C, inner ring outer diameter ΦD1 value, inner ring raceway R value, outer ring diameter ΦM value and other related parameters of the self-aligning ball bearing standard part 9 shown;

[0049] calculate Figure 3 The raceway outer diameter ΦD2 value of the inner ring 5 of the special bearing shown is obtained by subtracting the active amount 0.05mm from the calculated raceway outer diameter ΦD2 value as required to obtain the raceway outer diameter ΦD2 in the processing drawing;

[0050] prepared by Figure 3 The processing flow of the special bearing inner ring 5 shown is to prepare the raw materials and organize the production according to the processing flow;

[0051] Balance test, according to the balance test requirements Figure 3 The material is removed from the middle W surface to ensure the unbalance of the inner ring 5 of the processed special bearing, for example, 3g.mm;

[0052] The balls, outer rings and ball cages of the self-aligning ball bearing standard parts 9 and the special bearing inner ring 5 are assembled to obtain the special bearing, which is then inspected for quality and put into use.

[0053] Calculation and processing method of the size of the inner ring 5 of the special bearing in the balancing device:

[0054] (1) Measurement Figure 4 The ball diameter Φd in the self-aligning ball bearing standard part 9 shown in the figure is Figure 3 The inner ring bearing raceway center distance C, inner ring outer diameter ΦD1, and inner ring raceway R value are shown;

[0055] (2) Calculation Figure 3 The outer diameter ΦD2 value of the inner ring 5 of the special bearing is Figure 3 After the correction required by Technical Condition 3, the corrected value shall be added to the processing drawing of the inner ring 5 of the special bearing. Figure 3 The technical requirements are:

[0056] 1. ΦD1 is manufactured according to the measured dimensions of the inner ring of the ball bearing.

[0057] 2. ΦD2, C, R are manufactured according to the average value of the actual measured ball bearing inner ring raceway dimensions.

[0058] 3. Fine-tune ΦD2 to correct the diameter movement, and the allowable movement is 0.03~0.06mm.

[0059] 4. The runout of the two raceways R to ΦA is 0.005max.

[0060] 5. The parallelism between the two raceways R is 0.005.

[0061] 6. The runout of the remaining surfaces to ΦA is 0.1.

[0062] 7. Remove material from the W surface to ensure that the part imbalance is 3g.mm.

[0063] Measure the outer diameter of the inner ring of the self-aligning ball bearing standard 9 in three sections in the axial direction (i.e. the direction of the nominal width B of the bearing) and record them as Φd1, Φd2, and Φd3. The average value is determined according to the following formula Figure 3 The ΦD1 value is obtained from the processing drawing value of the inner ring 5 of the special bearing;

[0064] ΦD1=(Φd1+Φd2+Φd3) / 3;

[0065] (3) Measure the ball diameter Φd and record it. The maximum diameter difference of each row of balls must be 0.002 mm.

[0066] (4) Measurement Figure 4The ΦD and ΦM values ​​on the outer ring of the self-aligning ball bearing standard part 9 are shown, where ΦD is used for matching with the inner hole of the first bearing seat 4 (this value is used as the inner ring outer diameter ΦD1 of the inner ring of the special bearing), ensuring the interference fit requirement between the outer ring of the self-aligning ball bearing standard part 9 and the inner hole of the first bearing seat 4;

[0067] (5) Calculate and determine based on the inner ring bearing raceway center distance C, inner ring raceway R value and outer ring diameter ΦM Figure 3 The outer diameter ΦD2 value of the inner ring 5 of the special bearing;

[0068] The calculation process is as follows: Figure 5 As shown:

[0069] In right triangle OAB: AC=AB-BC;

[0070]

[0071] It is known that: OA=C / 2, BC=Φd / 2, OB=(ΦM-Φd) / 2.

[0072] Substituting it in, we can get:

[0073] (6) Press Figure 3 The technical condition 3 shown requires that the calculated value of the outer diameter ΦD2 of the inner ring 5 of the special bearing be subtracted from the active amount of 0.05 mm and applied to the processing drawing;

[0074] (7) Prepare the processing flow of the special bearing inner ring 5, as follows:

[0075] 1) Sleeper car: Made of bar material, the entire surface of the car (including Figure 3 The stepped inner hole of the inner ring 5 of the special bearing, the stepped surface of the inner hole, the two axial end faces of the inner ring 5 of the special bearing and the outer cylindrical surface of the inner ring 5 of the special bearing, each surface has a single-side allowance for grinding;

[0076] 2) Surface grinding: Grind the two end faces of the inner ring of the special bearing with an axial length of 5 on a surface grinder, leaving 0.4mm on one side to ensure the parallelism of the two end faces;

[0077] 3) Horizontal machining center: alignment and Figure 3 Drill 4-Φ8 on the outer surface of the middle left end. This step is optional.

[0078] 4) Fitter: deburring and rounding of sharp edges;

[0079] 5) Heat treatment: after quenching and tempering, ensure that the surface hardness meets HRC58-64;

[0080] 6) Surface grinding: Grind the two end faces of the axial length of the inner ring 5 of the special bearing on a surface grinder, leaving a single-side margin to ensure the parallelism of the two end faces;

[0081] 7) Precision internal grinding: Fine grinding of the inner hole surfaces and corresponding end surfaces of the inner ring 5 of the special bearing, with single-side margins still left on each surface;

[0082] 8) Artificial aging treatment;

[0083] 9) Surface grinding: Grind the two end faces of the axial length of the inner ring of the special bearing 5 on a surface grinder, leaving a single-side margin to ensure the parallelism of the two end faces;

[0084] 10) bluing;

[0085] 11) Fitter: Grind the two end faces of the axial length of the inner ring 5 of the special bearing to meet the parallelism and flatness requirements of the two end faces in the drawing;

[0086] 12) Precision internal grinding: Grind the inner hole surfaces and corresponding end surfaces (including the step surface that matches the axial end surface of the journal) of the inner ring 5 of the special bearing to ensure that the cylindricity and runout of the inner hole that matches the journal meet the requirements;

[0087] 13) CNC external grinding: grinding the outer cylindrical surface of the inner ring 5 of the special bearing and the corresponding end surface to ensure Figure 3 Technical requirements 4 and 5;

[0088] 14) Balance test: Figure 3 The technical conditions shown require 7 Figure 3 Material is removed from the W surface to ensure that the unbalance is 3g.mm.

[0089] (10) Prepare raw materials according to the above process and organize the production of special bearing inner ring 5;

[0090] (11) Quality inspection and delivery for subsequent assembly of special bearings.

[0091] The method for the low-pressure turbine rotor balancing test is as follows:

[0092] like Figure 1 As shown in the figure, the special bearing is assembled from the left side of the low-pressure turbine rotor, and the low-pressure turbine rotor Φd2 journal is connected to the Figure 3 The special bearing inner ring 5 shown is positioned in correspondence with the inner hole ΦA, and the low-pressure turbine rotor is axially locked by the first clamping nut 7, the second clamping nut 8, the external thread on the shaft surface on one side of the low-pressure turbine rotor shaft neck, and the end face of the special bearing inner ring 5; the positioning, clamping and fixing between the first bearing seat 4 and the balancing machine are achieved through the mounting groove with a width of H1 and an outer diameter of Φd.

[0093] Axial and radial positioning is achieved through the outer diameter Φd1 and end face of the bearing seat bushing 3 cooperating with the inner hole of the right end bearing of the low-pressure turbine rotor; positioning, clamping and fixing with the balancing machine are achieved through the mounting groove with a width of H and an outer diameter of Φd on the second bearing seat 1.

[0094] The contents not described in detail in the specification of the present invention belong to the prior art known to the professional and technical personnel in the field. Although the illustrative specific embodiments of the present invention are described above to facilitate the understanding of the present invention by the technical personnel in the field, it should be clear that the present invention is not limited to the scope of the specific embodiments. For ordinary technicians in the field of this technology, as long as various changes are within the spirit and scope of the present invention defined and determined by the attached claims, these changes are obvious, and all inventions and creations using the concept of the present invention are protected.

Claims

1. A low-pressure turbine rotor balancing device, characterized in that: It includes a first positioning and clamping component connected to the shaft journal of the low-pressure turbine rotor, and a second positioning and clamping component connected to the inner hole of the low-pressure turbine rotor bearing, wherein: The first positioning and clamping component comprises a first bearing seat (4), the circumferential surface of the first bearing seat (4) is provided with a mounting groove for positioning with a balancing machine, a self-aligning ball bearing standard component (9) without an inner ring is installed in the inner hole of the first bearing seat (1), the inner ring of the self-aligning ball bearing standard component (9) is replaced with a special bearing inner ring (5), and the axial end surface of the first bearing seat (1) is connected to a bearing pressing ring (6) for pressing the self-aligning ball bearing standard component (9); The special bearing inner ring (5) comprises an inner hole matched with the low-pressure turbine rotor shaft neck, an inner hole step surface matched with the axial end face of the low-pressure turbine rotor shaft neck, a surface raceway matched with the ball of the self-aligning ball bearing standard part (9), and a cylindrical surface located outside the inner hole of the first bearing seat (4) and used to adjust the unbalance amount of the special bearing inner ring (5); The second positioning and clamping component comprises a second bearing seat (1), the circumferential surface of the second bearing seat (1) is provided with a mounting groove for positioning with a balancing machine, a bearing seat spindle (2) is installed in the inner hole of the second bearing seat (1) and is plugged into the inner hole of a low-pressure turbine rotor bearing, a bearing seat sleeve (3) is installed at the end of the bearing seat spindle (2), and the end of the bearing seat spindle (2) is matched with the inner hole of the low-pressure turbine rotor bearing through the bearing seat sleeve (3).

2. A low-pressure turbine rotor balancing device according to claim 1, characterized in that: Also includes: A first clamping nut (7) and a second clamping nut (8), wherein the first clamping nut (7) and the second clamping nut (8) are connected to the external thread of the shaft surface on one side of the low-pressure turbine rotor shaft neck, and the first clamping nut (7) or the second clamping nut (8) is clamped on the end face of the inner ring (5) of the special bearing located on the outer side of the first bearing seat (4).

3. A low-pressure turbine rotor balancing device according to claim 1, characterized in that: It also includes a special hexagonal bolt (12), which passes through the second bearing seat (1) and points to the low-pressure turbine rotor bearing.

4. A method for processing a special bearing inner ring as claimed in claim 1, characterized in that: The following steps are involved: Step 1, disassembling the self-aligning ball bearing standard part (9), removing the inner ring, and retaining the balls, ball cage and outer ring; Step 2, obtaining various parameters of the self-aligning ball bearing standard part (9) in step 1, including the ball diameter Φd, the inner ring bearing raceway center distance C, the inner ring outer diameter ΦD1, the inner ring raceway R value, the bearing nominal width B and the outer ring raceway diameter ΦM value; Step 3, based on the parameters of the self-aligning ball bearing standard part (9) obtained in step 2, calculate the outer diameter ΦD2 of the raceway of the inner ring (5) of the special bearing; Step 4, processing the special bearing inner ring (5) according to the outer diameter Φd2 of the low-pressure turbine rotor shaft neck, the outer diameter ΦD2 of the raceway of the special bearing inner ring (5), the center distance C of the inner ring bearing raceway, the ball diameter Φd and the nominal width B of the bearing; Step 5, performing a dynamic balancing test on the processed special bearing inner ring (5), and obtaining an unbalance amount that meets the requirements by removing material from the cylindrical surface of the special bearing inner ring (5) used for adjusting the unbalance amount; Step six, assembling the special bearing inner ring (5) that meets the unbalance requirement in step five as the bearing inner ring with the balls, ball cage and outer ring of the self-aligning ball bearing standard part (9) in step one.

5. The method for processing the inner ring of a special bearing according to claim 4, characterized in that: In the step three, the outer diameter ΦD2 of the raceway of the inner ring (5) of the special bearing obtained by calculation is subtracted from an active amount to obtain the final value of the outer diameter ΦD2 of the raceway of the inner ring (5) of the special bearing processed in the step four.

6. The method for processing the inner ring of a special bearing according to claim 4, characterized in that: In step 4, the processing steps of the special bearing inner ring (5) include: Step 1, using bar stock, turning all surfaces and leaving a single-side allowance, all surfaces including the end face, inner hole and outer cylindrical surface of the special bearing inner ring (5); Step 2, grinding two end faces of the axial length of the inner ring (5) of the special bearing using a grinder; Step 3: remove burrs and round off sharp edges; Step 4: quenching and tempering; Step 5, grinding the two end faces of the axial length of the inner ring (5) of the special bearing again, leaving a single-side margin; Step 6, fine grinding each surface of the inner hole of the inner ring (5) of the special bearing and the corresponding end surface, leaving a single-side margin on each surface; Step seven, artificial aging; Step 8, grinding the two end faces of the axial length of the inner ring (5) of the special bearing again, leaving a single-side margin; Step nine, bluing; Step 10, grinding the two end faces of the axial length of the inner ring (5) of the special bearing again; Step 11, fine grinding each surface of the inner hole and the corresponding end surface of the inner ring (5) of the special bearing; Step 12, grinding the outer circumferential surfaces and corresponding end surfaces of the inner ring (5) of the special bearing; Step 13, balancing test, removing the material on the cylindrical surface of the inner ring (5) of the special bearing for adjusting the unbalance amount, and obtaining the unbalance amount that meets the requirements.

7. A low-pressure turbine rotor balancing test method, characterized in that: The balancing device according to claim 2 is adopted, and comprises: The outer cylindrical surface of the low-pressure turbine rotor shaft neck is matched with the inner hole of the inner ring of the special bearing (5), and the axial end face of the shaft neck is positioned with the inner hole step surface of the inner ring of the special bearing (5). The low-pressure turbine rotor is axially locked by the first clamping nut (7), the second clamping nut (8), the shaft surface external thread on one side of the low-pressure turbine rotor shaft neck and the end face of the inner ring of the special bearing (5), and is positioned, clamped and fixed with a balancing machine by the mounting groove on the first bearing seat (4); Axial and radial positioning is performed by the cooperation of the bearing seat bushing (3) and the inner hole of the low-pressure turbine rotor bearing, and positioning, clamping and fixing with the balancing machine are performed by the mounting groove on the second bearing seat (1).

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