CN214373311U - Accurate centering structure for vertical rotor tester - Google Patents
Accurate centering structure for vertical rotor tester Download PDFInfo
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- CN214373311U CN214373311U CN202120606907.8U CN202120606907U CN214373311U CN 214373311 U CN214373311 U CN 214373311U CN 202120606907 U CN202120606907 U CN 202120606907U CN 214373311 U CN214373311 U CN 214373311U
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- spigot
- transition flange
- flange
- speed increaser
- shell
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Abstract
The utility model discloses an accurate centering structure is used to vertical rotor tester, make eccentric structure's transition flange through tang about adopting, the transition flange circles all has a plurality of long circular arc flange holes, the flange hole is non-eccentric structure, there is the phase relation between transition flange's the protruding tang in upper portion and the concave tang of the lower part of increaser, there is the phase relation between the lower concave tang of transition flange and the protruding tang of casing upper portion, there is the phase relation between the concave tang of middle part and the protruding tang of bearing frame in the casing, through adjusting the different phase relation of these three departments, reduce or compensate because the inevitable decentraction error that produces with the assembly between increaser output shaft and the casing transmission shaft. The concentricity adjusting device has the advantages that parts do not need to be disassembled and repaired many times, machining precision and assembling precision do not need to be improved, special detection tools and methods do not need to be used, concentricity can be adjusted conveniently, zero can be achieved theoretically, rotor vibration is reduced, and rotor stability is improved.
Description
Technical Field
The utility model belongs to the technical field of machinery, mainly relate to vertical rotor tester, more mainly relate to an accurate centering fine setting structure.
Background
The rotor with the rotating speed exceeding 10000rpm is generally called as an ultra-high speed rotor, the processing precision and the assembly precision of ultra-high speed rotor parts directly influence the rotating performance of the rotor, axial or radial deflection among the rotating parts can cause deviation from a rotating axis, very large centrifugal force is generated, rotor vibration is caused, the rotating parts are damaged, the rotating speed of the rotor cannot reach the expected value, and other serious problems, so that the key point is to ensure the concentricity of the assembled parts.
Since machining and manufacturing errors and assembly errors of each component are inevitable, if the ultra-high speed rotor structure is relatively complicated, the coaxiality of the rotor cannot be ensured only from the aspect of improving machining and assembly accuracy. The existing processing technology and level can not greatly improve the processing precision of parts. The existing solution is to improve the assembly accuracy or guide the assembly by using an assembly testing technology, thereby improving the assembly accuracy of the rotor mechanism.
Luo Xin precision parts, Inc. proposed a coaxiality measuring apparatus (a coaxiality measuring instrument, publication No. CN 202024752U). The coaxiality and the runout degree of the existing precise parts are mainly measured, but the problem of coaxiality deviation existing after the rotor is assembled is not solved.
The university of Xian transportation proposes a method for detecting the assembly performance of an aircraft engine rotor (a method for detecting the assembly performance of the aircraft engine rotor, publication number: CN 101799354A). The method is mainly used for judging whether the assembly of the rotor of the aircraft engine is qualified or not and whether rework and repair are needed or not, but only scrapping treatment can be carried out on parts which still cannot meet the coaxiality requirement in repeated rework and repair, so that the assembly efficiency is influenced, and the cost is wasted due to scrapping of the parts.
The Harbin industry university proposes an aircraft engine rotor assembly method and device based on multi-component concentricity optimization (an aircraft engine rotor assembly method and device based on multi-component concentricity optimization, publication number: CN 103790648B). The method mainly obtains the assembly error of each rotor through measurement, analyzes the influence weight of each rotor on the coaxiality of the assembled rotor, optimizes the weight to obtain the assembly parameters of each rotor, and further guides the assembly of the rotors. However, the problem of misalignment of the coaxiality still exists when the best assembly accuracy is achieved, and the above patent does not propose a solution to this problem.
The eccentricity or inclination errors of all parts of the ultra-high speed rotor are accumulated, so that the excessive deflection and inclination of the whole assembled rotor can be caused, and the coaxiality deviation of the rotor is large. The superspeed rotor test bed produced at present in China often has the problems of serious deflection of a rotating shaft, large centrifugal force and serious vibration due to the fact that rotating parts are not concentric, and finally the rotating shaft is seriously damaged and twisted off when the rotating speed is increased to more than 10000rpm in a rotor test.
The ultra-high speed rotor assembly is generally manually assembled, and a dial indicator is used for manual measurement. The assembly needs to be carried out by cooperation of skilled technicians and workers with abundant experience, and the optimal assembly position can be found by assembling and disassembling the parts for multiple times and repairing the parts for multiple times. If the rotor structure is complex, the rotor still has coaxiality deviation when in the optimal assembly position, and no effective solution exists for the problem of the coaxiality deviation under the condition, so that the mounting efficiency of the rotor is low, and the coaxiality is poor after the assembly, thereby influencing the performance of the ultra-high-speed rotor.
SUMMERY OF THE UTILITY MODEL
Aiming at the defects in the prior art, a precise centering fine adjustment structure and an adjustment method are provided to solve the problems that the coaxiality of the assembled ultrahigh-speed rotor is low and cannot be adjusted, and the purposes that the coaxiality of the assembled ultrahigh-speed rotor is high, the vibration is small, the installation is easy, the adjustment is convenient, and the performance of the ultrahigh-speed rotor is improved are achieved.
The purpose of the utility model is realized like this:
a transition flange and a speed increaser are connected and fastened together through screws; the output shaft of the speed increaser is sleeved in the central through hole of the transition flange; the output shaft of the speed increaser is connected with the transmission shaft through a rigid sleeve;
the upper convex spigot and the lower concave spigot of the transition flange are both in eccentric structures; the misalignment amount between the output shaft of the speed increaser and the lower female spigot of the speed increaser is e1, the misalignment amount between the upper female spigot of the shell and the transmission shaft is e2, the theoretical eccentric amount of the upper male spigot of the transition flange is e3, the theoretical eccentric amount of the lower female spigot of the transition flange is e4, and the condition | e3-e4| e1-e2| needs to be met; the diameter of the upper convex spigot of the transition flange is matched with the diameter of the lower concave spigot of the speed increaser; the diameter of the lower concave spigot of the transition flange is matched with the diameter of the upper convex spigot of the shell;
the matching means that the sizes are the same and the two are in clearance fit.
The transition flange is provided with a plurality of evenly distributed flange holes on the periphery, the flange holes are long circular arc-shaped holes, the flange holes are of non-eccentric structures, and the transition flange and the speed increaser are connected and fastened together through screws penetrating through the long circular arc-shaped holes.
The diameter size of the concave spigot at the middle part of the shell is matched with the diameter size of the convex spigot of the bearing seat, the transmission shaft, the bearing end cover and the bearing seat are assembled into a bearing seat assembly body, and the bearing seat assembly body is connected and fastened with the shell through screws.
The transition flange has a phase relation with the lower concave spigot of the speed increaser, and the transition flange is continuously rotated and adjusted within a certain angle range clockwise or anticlockwise by utilizing a process threaded hole relative to the speed increaser so as to compensate the non-concentricity between the output shaft of the speed increaser and the lower concave spigot of the speed increaser.
The phase relation exists between the concave spigot at the lower part of the transition flange and the convex spigot at the upper part of the shell, and relative to the transition flange, the shell is rotationally adjusted at a fixed angle clockwise or anticlockwise so as to eliminate or reduce the non-concentricity of the output shaft of the speed increaser and the transmission shaft.
A transition flange is adopted, and a convex spigot at the upper part and a concave spigot at the lower part of the transition flange are both in eccentric structures; the misalignment amount between the output shaft of the speed increaser and the lower female spigot thereof is e1, the misalignment amount between the upper female spigot of the shell and the transmission shaft is e2, the theoretical eccentric amount of the upper male spigot of the transition flange is determined to be e3, the theoretical eccentric amount of the lower female spigot of the transition flange is determined to be e4, and the condition | e3-e4| e1-e2| needs to be met; the diameter of the upper male spigot of the transition flange is matched with the diameter of the lower female spigot of the speed increaser, wherein the matching means that the two are the same in size, but are in clearance fit, and the lower part is the same; the diameter of the lower concave spigot of the transition flange is matched with the diameter of the upper convex spigot of the shell; the output shaft of the speed increaser and the transmission shaft transmit torque through the rigid sleeve;
the phase relation exists between the upper convex spigot of the transition flange and the lower concave spigot of the speed increaser, and relative to the speed increaser, the transition flange continuously rotates and adjusts within a certain angle range clockwise or anticlockwise so as to compensate the non-concentricity between the output shaft of the speed increaser and the lower concave spigot of the speed increaser;
a phase relation exists between the concave spigot at the lower part of the transition flange and the convex spigot at the upper part of the shell, and relative to the transition flange, the shell is rotationally adjusted at a fixed angle clockwise or anticlockwise so as to eliminate or reduce the non-concentricity between the output shaft of the speed increaser and the transmission shaft.
Compared with the prior art, the utility model has the advantages that: the utility model discloses a flange that eccentric structure was made to tang about adopting, the flange hole has a plurality of long circular arc flange holes on the flange circle, the flange hole is non-eccentric structure, there is the phase relation between flange's the protruding tang in upper portion and the concave tang in lower part of increaser, there is the phase relation between flange lower recess tang and the protruding tang in casing upper portion, there is the phase relation between the concave tang in middle part and the protruding tang of bearing frame in the casing, through adjusting the different phase relation of these three departments, reduce or compensate because the inevitable decentraction error that produces with the assembly between increaser output shaft and the casing transmission shaft. The concentricity adjusting device has the advantages that parts do not need to be disassembled and repaired many times, machining precision and assembling precision do not need to be improved, special detection tools and methods do not need to be used, concentricity can be adjusted conveniently, zero can be achieved theoretically, rotor vibration is reduced, and rotor stability is improved.
Drawings
Fig. 1 is a schematic structural view of the present invention;
FIG. 2 is a sectional view taken along line A-A of FIG. 1;
FIG. 3 is a cross-sectional view taken at the location B-B of FIG. 1;
FIG. 4 shows the structure of the speed increaser and the output shaft;
FIG. 5 is a view taken along line A of FIG. 4;
FIG. 6 is a schematic structural view of a transition flange;
FIG. 7 is a cross-sectional view taken at the position C-C of FIG. 6;
FIG. 8 is a schematic view of the housing structure;
FIG. 9 is a top view of FIG. 8;
FIG. 10 is a schematic view of a bearing seat structure;
FIG. 11 is a top view of FIG. 10;
the part numbers in the figure are: 1-speed increaser, 101-speed increaser output shaft, 102-speed increaser lower part coupling screw hole, 110-speed increaser lower part concave spigot, 2-steel sleeve, 3-transition flange, 301-flange hole of transition flange, 302-transition flange rotary adjusting process screw hole, 310-transition flange upper part convex spigot, 320-transition flange lower part concave spigot, 4-shell, 401-shell upper part flange hole, 410-shell upper part convex spigot, 420-shell middle part concave spigot, 5-drive shaft, 6-bearing seat, 601-bearing seat flange hole, 610-bearing seat convex spigot, 7-screw.
Detailed Description
The present invention will be described in detail with reference to the accompanying drawings, wherein, as shown in the drawings, the transition flange 3 is fastened to the speed increaser 1 by screw connection; an output shaft 101 of the speed increaser is sleeved in a central through hole of the transition flange; the output shaft of the speed increaser is connected with the transmission shaft through a rigid sleeve 2;
the utility model adopts the transition flange 3, and the upper convex seam allowance 310 and the lower concave seam allowance 320 of the transition flange are both eccentric structures;
the misalignment amount between the output shaft 101 of the speed-increasing gear and the lower female spigot 110 thereof is obtained by pre-assembly measurement as e1, the misalignment amount between the upper female spigot 410 of the housing and the transmission shaft 5 is obtained by pre-assembly measurement as e2, the theoretical eccentricity of the upper male spigot 310 of the transition flange is determined as e3, the theoretical eccentricity of the lower female spigot 320 of the transition flange is determined as e4, and the condition | e3-e4| -e 1-e2|, is satisfied. The diameter of the upper male spigot 310 of the transition flange is matched with the diameter of the lower female spigot 110 of the speed increaser, wherein the matching means that the two are the same in size, clearance fit and the same in the lower part; the lower female tang 320 of the transition flange is sized to match the diameter of the upper male tang 410 of the housing. A plurality of evenly distributed flange holes 301 are formed in the periphery of the transition flange, the flange holes 301 are long circular arc-shaped holes and are countersunk holes, the countersunk depth is larger than the thickness of a screw head of a screw 9 installed at the position, the flange holes 301 are of a non-eccentric structure, the number of the flange long circular holes 301 is 8 in the embodiment, and the angle of each long circular hole 301 is 22.5 degrees. The transition flange 3 and the speed increaser 1 are fixedly connected through a plurality of screws 9 which are spaced by 180 degrees, and the number of the screws 9 is 2 in the embodiment. The transition flange 3, the speed increaser 1 and the shell 4 are fixedly connected together through screws 7, and the number of the screws 7 is 6 in the embodiment. The diameter size of the concave spigot 420 in the middle of the shell is matched with the diameter size of the convex spigot 610 of the bearing seat, the transmission shaft 5, the bearing end cover and the bearing seat 6 are assembled into a bearing seat assembly, and the bearing seat assembly is connected and fastened with the shell 4 through a screw 8. The output shaft 101 of the speed increaser is connected with the transmission shaft 5 through the profile of the rigid sleeve 2 to transmit torque. The phase relation exists between the upper convex spigot 310 of the transition flange and the lower concave spigot 110 of the speed increaser, relative to the speed increaser 1, the transition flange 3 utilizes the process threaded hole 302 to continuously rotate and adjust within a certain angle range clockwise or anticlockwise (namely alpha/2, alpha is the angle of the long circular arc flange hole 301 of the transition flange) so as to compensate the non-concentricity between the output shaft 101 of the speed increaser and the lower concave spigot 110 thereof, theoretically, the concentricity can be adjusted to 0mm, and the continuous rotation adjusting range of the transition flange 3 in the clockwise or anticlockwise direction can reach 11.25 degrees. The phase relation exists between the concave spigot 320 at the lower part of the transition flange and the convex spigot 410 at the upper part of the shell, and relative to the transition flange 3, the shell 4 is adjusted by rotating at a fixed angle clockwise or anticlockwise (namely 360 degrees/n, n is the number of the flange holes 401 at the upper part of the shell) so as to eliminate or reduce the non-concentricity between the output shaft 101 of the speed increaser and the transmission shaft 5, theoretically, the concentricity can be adjusted to be 0mm, and the fixed angle of the shell 4 adjusted by rotating clockwise or anticlockwise in the embodiment is 22.5 degrees. There is a phase relation between the concave spigot 420 in the middle part in the casing and the convex spigot 610 of the bearing seat, and for the casing 4, the bearing seat assembly is adjusted by rotating at a fixed angle clockwise or counterclockwise (i.e. 360 °/m, where m is the number of the flange holes 601 of the bearing seat) to reduce the concentricity between the convex spigot 410 on the upper part of the casing and the transmission shaft 5, and the fixed angle of the bearing seat assembly adjusted by rotating clockwise or counterclockwise in this embodiment is 45 °. The purpose of eliminating or reducing the inevitable non-concentricity error between the output shaft 101 of the speed increaser and the transmission shaft 5 of the shell due to manufacturing and assembling is achieved by adjusting different phase relations of the three parts, and the concentricity error can be adjusted to 0mm theoretically.
Claims (4)
1. The utility model provides a vertical rotor is accurate centering structure for tester which characterized in that: the transition flange is connected and fastened with the speed increaser through a screw; the output shaft of the speed increaser is sleeved in the central through hole of the transition flange; the output shaft of the speed increaser is connected with the transmission shaft through a rigid sleeve;
the upper convex spigot and the lower concave spigot of the transition flange are both in eccentric structures; the misalignment amount between the output shaft of the speed increaser and the lower female spigot of the speed increaser is e1, the misalignment amount between the upper female spigot of the shell and the transmission shaft is e2, the theoretical eccentric amount of the upper male spigot of the transition flange is e3, the theoretical eccentric amount of the lower female spigot of the transition flange is e4, and the condition | e3-e4| e1-e2| needs to be met; the diameter of the upper convex spigot of the transition flange is matched with the diameter of the lower concave spigot of the speed increaser; the diameter of the lower concave spigot of the transition flange is matched with the diameter of the upper convex spigot of the shell;
the diameter size of the concave spigot at the middle part of the shell is matched with that of the convex spigot of the bearing seat, the transmission shaft is arranged in the bearing, and the bearing is fixed in the bearing seat by the bearing end cover; the transmission shaft, the bearing end cover and the bearing seat are assembled into a bearing seat assembly, and the bearing seat assembly and the shell are connected and fastened together through screws.
2. The vertical rotor tester uses accurate centering structure according to claim 1, characterized in that: the transition flange is provided with a plurality of evenly distributed flange holes on the periphery, the flange holes are long circular arc-shaped holes, the flange holes are of non-eccentric structures, and the transition flange and the speed increaser are connected and fastened together through screws penetrating through the long circular arc-shaped holes.
3. The vertical rotor tester uses accurate centering structure according to claim 1, characterized in that: the transition flange has a phase relation with the lower concave spigot of the speed increaser, and the transition flange is continuously rotated and adjusted within a certain angle range clockwise or anticlockwise by utilizing a process threaded hole relative to the speed increaser so as to compensate the non-concentricity between the output shaft of the speed increaser and the lower concave spigot of the speed increaser.
4. The vertical rotor tester uses accurate centering structure according to claim 1, characterized in that: the phase relation exists between the concave spigot at the lower part of the transition flange and the convex spigot at the upper part of the shell, and relative to the transition flange, the shell is rotationally adjusted at a fixed angle clockwise or anticlockwise so as to eliminate or reduce the non-concentricity of the output shaft of the speed increaser and the transmission shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120606907.8U CN214373311U (en) | 2021-03-25 | 2021-03-25 | Accurate centering structure for vertical rotor tester |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202120606907.8U CN214373311U (en) | 2021-03-25 | 2021-03-25 | Accurate centering structure for vertical rotor tester |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN214373311U true CN214373311U (en) | 2021-10-08 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202120606907.8U Active CN214373311U (en) | 2021-03-25 | 2021-03-25 | Accurate centering structure for vertical rotor tester |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN214373311U (en) |
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2021
- 2021-03-25 CN CN202120606907.8U patent/CN214373311U/en active Active
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