CN107084819B - A kind of turbine pump flex rotor high-speed balancing quality consistency control method - Google Patents
A kind of turbine pump flex rotor high-speed balancing quality consistency control method Download PDFInfo
- Publication number
- CN107084819B CN107084819B CN201710221414.0A CN201710221414A CN107084819B CN 107084819 B CN107084819 B CN 107084819B CN 201710221414 A CN201710221414 A CN 201710221414A CN 107084819 B CN107084819 B CN 107084819B
- Authority
- CN
- China
- Prior art keywords
- rotor
- turbine pump
- speed balancing
- outside diameter
- turbine
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 37
- 238000006073 displacement reaction Methods 0.000 claims abstract description 55
- 238000012360 testing method Methods 0.000 claims description 35
- 230000036461 convulsion Effects 0.000 claims description 13
- 239000000411 inducer Substances 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 7
- 230000008569 process Effects 0.000 abstract description 7
- 230000003321 amplification Effects 0.000 abstract description 3
- 238000003199 nucleic acid amplification method Methods 0.000 abstract description 3
- 238000012797 qualification Methods 0.000 abstract description 2
- 238000000354 decomposition reaction Methods 0.000 description 8
- 238000013461 design Methods 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 239000003380 propellant Substances 0.000 description 4
- 230000003252 repetitive effect Effects 0.000 description 3
- MYMOFIZGZYHOMD-UHFFFAOYSA-N Dioxygen Chemical compound O=O MYMOFIZGZYHOMD-UHFFFAOYSA-N 0.000 description 2
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 2
- 238000010009 beating Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000001257 hydrogen Substances 0.000 description 2
- 229910052739 hydrogen Inorganic materials 0.000 description 2
- 239000007788 liquid Substances 0.000 description 2
- 238000003032 molecular docking Methods 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 241000208340 Araliaceae Species 0.000 description 1
- 235000005035 Panax pseudoginseng ssp. pseudoginseng Nutrition 0.000 description 1
- 235000003140 Panax quinquefolius Nutrition 0.000 description 1
- 238000005119 centrifugation Methods 0.000 description 1
- 239000012141 concentrate Substances 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 235000008434 ginseng Nutrition 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000011835 investigation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000005303 weighing Methods 0.000 description 1
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/30—Compensating imbalance
- G01M1/36—Compensating imbalance by adjusting position of masses built-in the body to be tested
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention provides a kind of turbine pump flex rotor high-speed balancing quality consistency control method, determine that the lumped mass disk outside diameter runout upper limit, shafting screw-down torque lower limit, rotor are to the moderate upper limit in turbine pump combined rotor assembling process.Overcome the significant drawback of existing method high-speed balancing effect consistency difference when shafting is assembled repeatedly-decomposed, the present invention controls the consistency of rotor balancing quality, vibration displacement level after rotor balancing is not influenced by shafting structure repeated disassembled and assembled, vibration displacement amplification coefficient < 1.2 after repeated disassembled and assembled, while improving turbo pump rotor high-speed balancing qualification rate and delivery efficiency.
Description
Technical field
The present invention relates to a kind of for high-speed turbine pump flex rotor in the high-speed balancing uniform quality repeated when assembling
The turbine pump combined rotor of property control method, especially liquid hydrogen liquid oxygen rocket engine.
Background technique
Space strategy status is competitively fought in the 21st century, countries in the world, manned space flight and deep space exploration activity again by
Update speed to attention, especially carrier rocket is accelerated, and space flight Push Technology is led to develop rapidly.
Key component of the oxyhydrogen engine turbine pump as conveying liquid hydrogen liquid oxygen, operating status directly affect rocket motor
The Performance And Reliability of machine complete machine.Currently, the working speed of oxyhydrogen engine turbine pump is generally higher both at home and abroad, frequently with work
Flex rotor design between one, second order even two, three rank critical speeds.Smooth working band of the high revolving speed to turbo pump rotor
Challenge is carried out, it is necessary to be balanced using high-speed balancing technique to it, so that rotor smooth running, amplitude under working speed
In design allowed band.For turbo pump rotor higher for working speed (> 40000r/min), due to high revolving speed band
The threshold vibration problem of crossing turns to the balance quality of high-speed balancing or even entire process and balance system and combination
More stringent requirements are proposed for safety of son etc..The high cost characteristics and height of liquid-propellant rocket engine military service object (carrier rocket)
Stability requirement, so that controlling its quality very harsh.Turbine pump combined rotor normally comprises shaft, inducer, centrifugation
The components such as wheel, turbine, axle sleeve, clamp nut, gasket, bearing, bearing, and the overall structure feature of turbine pump determines its turn
Son needs combined rotor being decomposed into part status after high-speed balancing, could carry out last general assembly with turbine pump case.
And (there are threaded connection, spline connection, positioning surface connection, cooperation includes since part matching relationship each in turbine pump shafting is complicated
Interference fit, transition fit and clearance fit), therefore after combined rotor repeatedly assembly-decomposition, since part cooperates in shafting
The small size change of relationship will certainly cause the balance quality of entire rotor-support-foundation system to change, and make the rotor balanced originally, vibrate position
It moves exceeded once again.Before this invention, liquid-propellant rocket engine field is still at home for high-speed balancing quality consistency control technology
Belong to blank, main problem existing for domestic other field high-speed balancing is exactly: the effect of high-speed balancing fills repeatedly in rotor
With-decompose after be decreased obviously, specifically, by the rotor of high-speed balancing, generally repeat assembly-decomposition it is primary after, mistake
Vibration displacement at critical speed usually obviously amplifies three times or more.And actually more than liquid-propellant rocket engine, rotating machinery
Quite a few rotor is required to be decomposed into part status after high-speed balancing and be reinstalled in mechanical hull in industry,
Therefore, the consistency control of high-speed balancing quality is the conspicuous contradiction of restriction rotating machinery running accuracy, running efficiency, and
At present without effective control method.
Summary of the invention
Technical problem solved by the present invention is overcome the deficiencies in the prior art, it is high to propose a kind of turbine pump flex rotor
Quick-action balance quality consistency control method overcomes existing high-speed balancing effect consistency when shafting is assembled repeatedly-decomposed
The significant drawback of difference, controls the consistency of rotor balancing quality, the vibration displacement level after rotor balancing is not by shafting knot
Structure assembly-decomposition influence (repeat assembly-decomposition after vibration displacement amplification coefficient < 1.2) repeatedly.
The technical solution of the invention is as follows: a kind of turbine pump flex rotor high-speed balancing quality consistency controlling party
Method includes the following steps:
Step 1: assembly turbine pump combined rotor, finds the impeller of pump, turbine and connecting flange of turbine pump combined rotor
Etc. lumped masses disk outside diameter runout minimum value P0,i, and to the angular relative position of each part of worm-gear combination rotor into
Row marking；Subscript 0 indicates outside diameter runout initial minimum, and i indicates i-th of lumped mass disk, to any turbine pump
Combined rotor, i=1,2 ..., n, n are positive integer；
Step 2: carrying out high-speed balancing test under the outside diameter runout minimum state that step 1 determines, obtains and turn
The vibration displacement A of son0；
Step 3: disassembly turbine pump combined rotor, each part are not ressembled to the layout line, gas-turbine-pump combination is still controlled
Closing the outside diameter runout of the lumped masses disk such as rotor impeller of pump, turbine and connecting flange, outside diameter runout is most into step 1
Small state of value carries out high-speed balancing test, records rotor vibration displacement A1；If A1>1.2A0, then turbine pump combined rotor is in height
Quick-action need to be assembled when balancing by the scribing line in step 1；Otherwise, turbine pump combined rotor is not needed in high-speed balancing by step
Scribing line assembly in rapid one；
Step 4: turbine pump combined rotor is ressembled, increase the outside diameter runout P of the 1st lumped mass disk0,1Extremely
Pj,1, keeping the outside diameter runout of other lumped mass disks is P0,2, P0,3..., P0,n, high-speed balancing test is carried out, is obtained
Rotor vibration displacement Aj+1,1；J is positive integer；
Step 5: j=j+1, repeats step 4, until rotor vibration displacement Aj+1,1>1.2A0, then determine to be used at this time
Guarantee the outside diameter runout upper limit P of the 1st lumped mass disk of rotor high-speed balancing quality consistencyj+1,1；
Step 6: keeping the outside diameter runout of preceding i-1 lumped mass disk adjusted constant, increase i-th of concentration
The jerk value P of quality disk0,iTo Pj,i, keeping i+1 to the outside diameter runout of n-th of lumped mass disk is P0,i+1...,
P0,n, high-speed balancing test is carried out, rotor vibration displacement A is obtainedj+1,i；
Step 7: j=j+1, repeats step 6, until rotor vibration displacement Aj+1,i>1.2A0, then determine to be used at this time
Guarantee the outside diameter runout upper limit P of i-th of lumped mass disk of rotor high-speed balancing quality consistencyj+1,i；I=i+1, when
When i > n, eight are entered step, otherwise return step six；
Step 8: if turbine pump combined rotor is that work turns between first critical speed and second order critical speed
Son enters step 15；If turbine pump combined rotor is rotor of the work more than second order critical speed, nine are entered step；
Step 9: beating according to the outer circle in step 1 at turbine pump combination impeller pump impeller, turbine and connecting flange
Measure minimum value P0i, shafting screw-down torque T0High-speed balancing test is ressembled and carried out to turbine pump combined rotor, is obtained and is turned
The vibration displacement A of sonT0；
Step 10: reducing shafting screw-down torque T0To Tk, high-speed balancing test is carried out, rotor vibration displacement A is obtainedTk, k
For positive integer；
Step 11: k=k+1, repeats step 10, until rotor vibration displacement ATk>1.2AT0, then determine to be used at this time
Guarantee the shafting screw-down torque lower limit T of rotor high-speed balancing quality consistencyk+1；
Step 12: being jumped according to the outer circle in step 1 at turbine pump combination impeller pump impeller, turbine and connecting flange
Momentum minimum value P0i, shafting screw-down torque T0, rotor is to moderate U0Turbine pump combined rotor is ressembled and carries out high speed and is moved
Blance test obtains the vibration displacement A of rotorU0；
Step 13: increasing rotor to moderate U0To Um, high-speed balancing test is carried out, rotor vibration displacement A is obtainedUm, m
For positive integer；
Step 14: m=m+1, repeats step 13, until rotor vibration displacement AUm>1.2AU0, then determine to use at this time
In guarantee rotor high-speed balancing quality consistency rotor to moderate upper limit Um+1；Enter step 16；
Step 15: the scribing line determined according to step 1, finally the lumped mass disk outside diameter runout upper limit that obtains into
The assembly of row turbine pump combined rotor, method terminate；
Step 16: the scribing line determined according to step 1, the lumped mass disk outside diameter runout upper limit finally obtained, axis
It is that screw-down torque lower limit, rotor carry out the assembly of turbine pump combined rotor to the moderate upper limit.
Each part of step 1 center shafting include shaft, inducer, centrifugal wheel, turbine, axle sleeve, clamp nut, gasket,
Bearing, bearing, wherein the rotary structure of outer diameter > 2.5 times axis outer diameter is lumped mass disk.
The outside diameter runout minimum value P of lumped mass disk in the step 10,iNo more than 0.05mm.
It is described Step 4: Step 5: in step 6 or step 7, the adjusting step of the outside diameter runout of lumped mass disk
No more than 0.005mm.
Turbine pump combines rotor axial system screw-down torque T in the step 90=7.5 × Major Diam.
In the step 10 or step 11, turbine pump combines rotor axial system screw-down torque TkAdjusting step be not more than T0/
100。
In the step 12, the rotor of turbine pump combined rotor is to moderate U0No more than the diameter of axle/600.
In the step 13 or step 14, the rotor of turbine pump combined rotor is to moderate UmAdjusting step be not more than
0.005mm。
The advantages of the present invention over the prior art are that:
(1) present invention improves turbo pump rotor high-speed balancing quality consistency, makes the high-speed balancing of combined rotor
Effect is not influenced by rotor assembly-decomposition.By high-speed balancing quality consistency control technology, turbo pump rotor can reach
After balance, although still being able to guarantee vibration displacement level at 120 μm hereinafter, much excellent by multiple assembly-decomposition repeatedly
Critical speed vibration displacement 300 is crossed in the turbo pump rotor of same dimension scale (Φ 300mm × 400mm~Φ 600mm × 700mm)
μm industry level (without consistency control).
(2) present invention improves turbo pump rotor high-speed balancing qualification rate and delivery efficiency.Whirlpool is judged in industry at present
The method of wheel pump rotor high-speed balancing consistency relies primarily on repetitive test, i.e. rotor passes through after high-speed balancing
It repeats assembly-decomposition and carries out field investigation, record the vibration displacement of rotor, and require < 300 μm, and whole process is not any
Control means are easier to that the underproof situation of repeatability occurs, need to re-start rotor high-speed balancing immediately, on the one hand
Cause balance quality out of control, another party also significantly reduces the delivery efficiency of product.
(3) high-speed balancing quality consistency control method of the present invention is applied, can achieve effective control combination
The purpose of vibration displacement scattered error after rotor dismounting, while also greatly improving the delivery efficiency of product.
Detailed description of the invention
Fig. 1 is high-speed balancing key process parameter provided by the invention；
Fig. 2 is that turbo pump rotor high-speed balancing quality provided by the invention dismounts consistency control flow；
Specific embodiment
The invention proposes influence the five of liquid-propellant rocket engine turbine pump combined rotor high-speed balancing quality consistency
Class technological parameter, abutted flange bolt and clamp nut screw-down torque, the concentricity of rotor docking, combined rotor including shafting
Mounting shift angle, the rigidity of high-speed balancing rocker and the assembly parameter of combined rotor of each part, as shown in Fig. 1, this five
In class parameter, mounting shift angle, dynamic balancing rocker rigidly belong to the adjustable controllable parameter of testing stand technique, and rotor docking is concentric
Degree, the screw-down torque of shafting clamp nut, combined rotor assembly parameter belong to product design parameter scope (value range), need
Its design rationality is determined by high-speed balancing technique.Theoretical and experimental study has been carried out for these parameters, has been finally obtained
High-speed balancing consistency control method proposed by the invention.
The assembly precision of combined rotor plays a decisive role to the result of high-speed balancing and dynamic balancing technics consistency.It is logical
Cross factor (such as wheel disc jerk value, degree of misaligning, power that research has been found that required control during combined rotor assembly
Square, assembly circumferential position etc.) different design conjunction requirement, it will lead to vibration data consistency during dynamic balancing repetitive test
It is bad.In fact, carrying out high speed in the case that assembly technology parameter does not reach requirement or in the case that assembly consistency is bad
The repetitive test that dynamic balancing and assembly rotor carry out is all nonsensical.
Carry out key process parameter thus to study the impact effect of flex rotor high-speed balancing, it is smart to dynamic balancing is promoted
Degree and control dynamic balancing repeat assembly consistency and are of great significance.According to the consistency control research process of attached drawing 2, deeply slap
Influence of the key process parameter difference to turbine pump high-speed balancing is held, it is available to make turbine pump high-speed balancing uniform quality
The technological parameter region of convergence that property is effectively controlled, i.e., the convergency value of the parameters such as P, T, U in attached drawing 2.Convergency value is as turbine pump
The key control parameter of quality consistency when high-speed balancing is tight in turbo pump rotor high-speed balancing and subsequent general assembly
Lattice are carried out according to above-mentioned technological parameter value, and carry out inspection record, after so just can guarantee turbo pump rotor high-speed balancing,
Its counterbalance effect can be still maintained when repeatedly assembling-decomposing repeatedly, as long as assembly control parameter reaches production engineering specifications,
Vibration displacement amount of the combined rotor after assembly-decomposition repeatedly just meets the control ability of amplification coefficient < 1.2.
As shown in Figure 1 and Figure 2, a kind of turbine pump flex rotor high-speed balancing quality consistency control method, including it is as follows
Step:
Step 1: assembly turbine pump combined rotor, finds the impeller of pump, turbine and connecting flange of turbine pump combined rotor
Etc. lumped masses disk outside diameter runout minimum value P0,i, and to the angular relative position of each part of worm-gear combination rotor into
Row marking；Subscript 0 indicates outside diameter runout initial minimum, and i indicates i-th of lumped mass disk, to any turbine pump
Combined rotor, i=1,2 ..., n, n are positive integer；Each part of step 1 center shafting include shaft, inducer, centrifugal wheel,
Turbine, axle sleeve, clamp nut, gasket, bearing, bearing, wherein the rotary structure of outer diameter > 2.5 times axis outer diameter is to concentrate
Quality disk.The outside diameter runout minimum value P of lumped mass disk in the step 10,iNo more than 0.05mm.
Step 2: carrying out high-speed balancing test under the outside diameter runout minimum state that step 1 determines, obtains and turn
The vibration displacement A of son0；
Step 3: disassembly turbine pump combined rotor, each part are not ressembled to the layout line, gas-turbine-pump combination is still controlled
Closing the outside diameter runout of the lumped masses disk such as rotor impeller of pump, turbine and connecting flange, outside diameter runout is most into step 1
Small state of value carries out high-speed balancing test, records rotor vibration displacement A1；If A1>1.2A0, then turbine pump combined rotor is in height
Quick-action need to be assembled when balancing by the scribing line in step 1；Otherwise, turbine pump combined rotor is not needed in high-speed balancing by step
Scribing line assembly in rapid one；
Step 4: turbine pump combined rotor is ressembled, increase the outside diameter runout P of the 1st lumped mass disk0,1Extremely
Pj,1, keeping the outside diameter runout of other lumped mass disks is P0,2, P0,3..., P0,n, high-speed balancing test is carried out, is obtained
Rotor vibration displacement Aj+1,1；J is positive integer；
Step 5: j=j+1, repeats step 4, until rotor vibration displacement Aj+1,1>1.2A0, then determine to be used at this time
Guarantee the outside diameter runout upper limit P of the 1st lumped mass disk of rotor high-speed balancing quality consistencyj+1,1；
Step 6: keeping the outside diameter runout of preceding i-1 lumped mass disk adjusted constant, increase i-th of concentration
The jerk value P of quality disk0,iTo Pj,i, keeping i+1 to the outside diameter runout of n-th of lumped mass disk is P0,i+1...,
P0,n, high-speed balancing test is carried out, rotor vibration displacement A is obtainedj+1,i；
Step 7: j=j+1, repeats step 6, until rotor vibration displacement Aj+1,i>1.2A0, then determine to be used at this time
Guarantee the outside diameter runout upper limit P of i-th of lumped mass disk of rotor high-speed balancing quality consistencyj+1,i；I=i+1, when
When i > n, eight are entered step, otherwise return step six；
For the step 4 into step 7, the adjusting step of the outside diameter runout of lumped mass disk is not more than 0.005mm.
Step 8: if turbine pump combined rotor is that work turns between first critical speed and second order critical speed
Son enters step 15；If turbine pump combined rotor is rotor of the work more than second order critical speed, nine are entered step；
Step 9: beating according to the outer circle in step 1 at turbine pump combination impeller pump impeller, turbine and connecting flange
Measure minimum value P0i, shafting screw-down torque T0High-speed balancing test is ressembled and carried out to turbine pump combined rotor, is obtained and is turned
The vibration displacement A of sonT0；Turbine pump combines rotor axial system screw-down torque T in the step 90=7.5 × Major Diam.
Step 10: reducing shafting screw-down torque T0To Tk, high-speed balancing test is carried out, rotor vibration displacement A is obtainedTk, k
For positive integer；
Step 11: k=k+1, repeats step 10, until rotor vibration displacement ATk>1.2AT0, then determine to be used at this time
Guarantee the shafting screw-down torque lower limit T of rotor high-speed balancing quality consistencyk+1；In the step 10 or step 11, turbine
Pump group closes rotor axial system screw-down torque TkAdjusting step be not more than T0/100。
Step 12: being jumped according to the outer circle in step 1 at turbine pump combination impeller pump impeller, turbine and connecting flange
Momentum minimum value P0i, shafting screw-down torque T0, rotor is to moderate U0Turbine pump combined rotor is ressembled and carries out high speed and is moved
Blance test obtains the vibration displacement A of rotorU0；In the step 12, the rotor of turbine pump combined rotor is to moderate U0Less
In the diameter of axle/600.
Step 13: increasing rotor to moderate U0To Um, high-speed balancing test is carried out, rotor vibration displacement A is obtainedUm, m
For positive integer；
Step 14: m=m+1, repeats step 13, until rotor vibration displacement AUm>1.2AU0, then determine to use at this time
In guarantee rotor high-speed balancing quality consistency rotor to moderate upper limit Um+1；Enter step 16；The step 13 or
In step 14, the rotor of turbine pump combined rotor is to moderate UmAdjusting step be not more than 0.005mm.
Step 15: in rotor high-speed balancing and turbine pump general assembly, the scribing line, the final acquisition that are determined according to step 1
The lumped mass disk outside diameter runout upper limit carry out the assembly of turbine pump combined rotor, method terminates；
Step 16: in rotor high-speed balancing and turbine pump general assembly, the scribing line, the final acquisition that are determined according to step 1
The lumped mass disk outside diameter runout upper limit, shafting screw-down torque lower limit, rotor to the moderate upper limit carry out turbine pump combination turn
Subassembly.
Embodiment 1:
In the turbo pump rotor for carrying out high-speed balancing quality consistency using the invention at present, one of rotor is
Turbo-driven two-stage centrifugal pump configuration, for the flex rotor more than second order critical speed of working, when high-speed balancing, axis
Fasten totally 4, lumped mass disk: first-stage centrifugal wheel, two-stage centrifugal wheel, the turbine disk, coupling of shaft system flange, i.e. i=4.The type whirlpool
It is as follows that the wheel pump rotor application present invention carries out the step of high-speed balancing quality consistency control:
1) turbine pump combined rotor is assembled at rotor first-stage centrifugal wheel, two-stage centrifugal wheel, turbine and connecting flange
Outside diameter runout minimum value P0,1=0.03mm, P0,2=0.05mm, P0,3=0.05mm, P0,4=0.03mm, and in shaft
Inducer, clamp nut, centrifugal wheel, axle sleeve, turbine, shaft angular relative position carry out marking；
2) high-speed balancing test is carried out, rotor vibration displacement situation A is recorded0=85 μm；
3) rotor is decomposed, is not assembled to the layout line then, but still controls jerk value to P0,1< 0.03mm, P0,2< 0.05mm,
P0,3< 0.05mm, P0,4< 0.03mm carries out high-speed balancing test, records rotor vibration displacement situation A1=255.3 μm；
4) A is compared0、A1Vibration displacement situation, A1=255 μm > 1.2 × A0(102 μm) determine that the type turbo pump rotor is high
Quick-action need to be assembled strictly by groove when balancing；
5) combined rotor is ressembled, and increases first-stage centrifugal wheel outside diameter runout P at this time0,1To P1,1=0.035mm, and protect
Hold two-stage centrifugal wheel, turbine, outside diameter runout P at connecting flange0,2< 0.05mm, P0,3< 0.05mm, P0,4< 0.03mm, then carry out
High-speed balancing test, records rotor vibration displacement situation A2=91 μm；
6) increase P repeatedlyj,1Value, until when j=9, first-stage centrifugal wheel jerk value P9,1=0.075mm, at this time rotor
Vibration displacement Aj+1=A10=108.5 μm > 1.2 × A0, it is determined that out guarantee rotor high-speed balancing quality consistency level-one from
Heart wheel jerk value maximum value=P9,1=0.075mm；
7) first-stage centrifugal wheel jerk value P is kept9,1=0.075mm is constant, is determined with same method by the 5th and step 6
The maximum control jerk value of two-stage centrifugal wheel jerk value, turbine jerk value and adapter flange is respectively as follows: P3,2=0.065mm, P7,3
=0.085mm, P4,4=0.05mm；The then bounce of the type turbo pump rotor high-speed balancing and when general assembly each lumped mass disk
Amount should meet: P9,1<0.075mm、P3,2< 0.065mm, P7,3< 0.085mm, P4,4<0.05mm；
8) due to the type turbo pump rotor be flex rotor of the work more than second order critical speed, again according to draw
Line, according to P0,1=0.03mm, P0,2=0.05mm, P0,3=0.05mm, P0,4The jerk value of=0.03mm assembles combined rotor,
Screw thread specification be M20, therefore assemble when shafting screw-down torque are as follows: T0=7.5 × 20=150Nm, and it is dynamic flat to carry out high speed
Weighing apparatus test, obtains the vibration displacement A of rotorT0=88 μm；
9) combined rotor is ressembled, and keeps P0,1=0.03mm, P0,2=0.05mm, P0,3=0.05mm, P0,4=
0.03mm is constant, reduces shafting screw-down torque T0To T1, high-speed balancing test is carried out, rotor vibration displacement A is obtainedT1=91 μ
m；
10) reduce T repeatedlykValue, until when k=10, shafting screw-down torque Tk=T10=135Nm, at this time rotor
Vibration displacement AT10=106.7 μm > 1.2 × A0, it is determined that guarantee the shafting pressing force of rotor high-speed balancing quality consistency out
Square minimum value=T10=135Nm；
11) again to the layout line, according to P0,1=0.03mm, P0,2=0.05mm, P0,3=0.05mm, P0,4=0.03mm's
Jerk value, T0=150Nm assembles combined rotor, and due to diameter=30mm of shaft, combined rotor turns when assembling
Son takes U to moderate0=30/600=0.05mm, and high-speed balancing test is carried out, obtain the vibration displacement A of rotorU0=92 μm；
12) combined rotor is ressembled, and keeps P0,1=0.03mm, P0,2=0.05mm, P0,3=0.05mm, P0,4=
0.03mm, T0=150Nm is constant, increases rotor to moderate U0To U1, high-speed balancing test is carried out, rotor oscillation position is obtained
Move AU1=99 μm；
13) increase U repeatedlymValue, until rotor is to moderate U when m=4m=U4=0.07mm, at this time rotor oscillation position
Move AU4=117.2 μm > 1.2 × A0, it is determined that guarantee the rotor of rotor high-speed balancing quality consistency to moderate maximum value out
=U4=0.07mm；
14) the technique ginseng for ensuring model turbine pump combined rotor high-speed balancing quality consistency control is finally obtained
Number: a) should press the scribing line assembly of the part on combined rotor when high-speed balancing and turbine pump general assembly；B) first-stage centrifugal wheel, second level from
Heart wheel, turbine, adapter flange outside diameter runout should meet P respectively9,1<0.075mm、P3,2< 0.065mm, P7,3< 0.085mm,
P4,4<0.05mm；C) shafting screw-down torque T answer>135Nm, rotor answer<0.07mm to moderate U.
The content that description in the present invention is not described in detail belongs to the well-known technique of those skilled in the art.
Claims (8)
1. a kind of turbine pump flex rotor high-speed balancing quality consistency control method, which comprises the steps of:
Step 1: assembly turbine pump flex rotor, finds the outside diameter runout of lumped mass disk of turbine pump flex rotor most
Small value P0,i, lumped mass disk includes impeller of pump, turbine and connecting flange, and to each part of turbine pump flex rotor
Angular relative position carries out marking；Subscript 0 indicates that outside diameter runout initial minimum, i indicate i-th of lumped mass circle
Disk, to any turbine pump flex rotor, i=1,2 ..., n, n is positive integer；
Step 2: carrying out high-speed balancing test under the outside diameter runout minimum state that step 1 determines, obtaining rotor
Vibration displacement A0；
Step 3: disassembly turbine pump flex rotor, each part are not ressembled to the layout line, still controls turbine pump flexibility and turn
The outside diameter runout of sub- lumped mass disk outside diameter runout minimum state into step 1, lumped mass disk include pump leaf
Wheel, turbine and connecting flange carry out high-speed balancing test, record rotor vibration displacement A1；If A1>1.2A0, then turbine pump
Flex rotor need to be assembled in high-speed balancing by the scribing line in step 1；Otherwise, turbine pump flex rotor is in high-speed balancing
When do not need by step 1 scribing line assembly；
Step 4: turbine pump flex rotor is ressembled, increase the outside diameter runout P of the 1st lumped mass disk0,1To Pj,1,
The outside diameter runout for keeping other lumped mass disks is P0,2, P0,3..., P0,n, high-speed balancing test is carried out, rotor is obtained
Vibration displacement Aj+1,1；J is positive integer；
Step 5: j=j+1, repeats step 4, until rotor vibration displacement Aj+1,1>1.2A0, then determined at this time for guaranteeing
The outside diameter runout upper limit P of 1st lumped mass disk of rotor high-speed balancing quality consistencyj+1,1；
Step 6: keeping the outside diameter runout of preceding i-1 lumped mass disk adjusted constant, increase i-th of lumped mass
The jerk value P of disk0,iTo Pj,i, keeping i+1 to the outside diameter runout of n-th of lumped mass disk is P0,i+1..., P0,n, into
The test of row high-speed balancing, obtains rotor vibration displacement Aj+1,i；
Step 7: j=j+1, repeats step 6, until rotor vibration displacement Aj+1,i>1.2A0, then determined at this time for guaranteeing
The outside diameter runout upper limit P of i-th of lumped mass disk of rotor high-speed balancing quality consistencyj+1,i；I=i+1 works as i > n
When, eight are entered step, otherwise return step six；
Step 8: if turbine pump flex rotor is rotor of the work between first critical speed and second order critical speed, into
Enter step 15；If turbine pump flex rotor is rotor of the work more than second order critical speed, nine are entered step；
Step 9: most according to the outside diameter runout in step 1 at turbine pump flex rotor impeller of pump, turbine and connecting flange
Small value P0i, shafting screw-down torque T0High-speed balancing test is ressembled and carried out to turbine pump flex rotor, obtains rotor
Vibration displacement AT0；
Step 10: reducing shafting screw-down torque T0To Tk, high-speed balancing test is carried out, rotor vibration displacement A is obtainedTk, k is positive
Integer；
Step 11: k=k+1, repeats step 10, until rotor vibration displacement ATk>1.2AT0, then determined at this time for guaranteeing
The shafting screw-down torque lower limit T of rotor high-speed balancing quality consistencyk+1；
Step 12: according to the outside diameter runout in step 1 at turbine pump flex rotor impeller of pump, turbine and connecting flange
Minimum value P0i, shafting screw-down torque T0, rotor is to moderate U0Turbine pump flex rotor is ressembled and carries out high-speed balancing
Test, obtains the vibration displacement A of rotorU0；
Step 13: increasing rotor to moderate U0To Um, high-speed balancing test is carried out, rotor vibration displacement A is obtainedUm, m is positive
Integer；
Step 14: m=m+1, repeats step 13, until rotor vibration displacement AUm>1.2AU0, then determined at this time for protecting
The rotor of rotor high-speed balancing quality consistency is demonstrate,proved to moderate upper limit Um+1；Enter step 16；
Step 15: the scribing line determined according to step 1, the lumped mass disk outside diameter runout upper limit finally obtained carry out whirlpool
The assembly of wheel pump flex rotor, method terminate；
Step 16: the lumped mass disk outside diameter runout upper limit, the shafting that according to the determining scribing line of step 1, finally obtain are twisted
Clamp force square lower limit, rotor carry out the assembly of turbine pump flex rotor to the moderate upper limit.
2. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 1, special
Sign is, each part of step 1 center shafting include shaft, inducer, centrifugal wheel, turbine, axle sleeve, clamp nut, gasket,
Bearing, bearing, wherein the rotary structure of outer diameter > 2.5 times axis outer diameter is lumped mass disk.
3. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 1 or 2,
It is characterized in that, the outside diameter runout minimum value P of lumped mass disk in the step 10,iNo more than 0.05mm.
4. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 1, special
Sign is, described Step 4: Step 5: in step 6 or step 7, the adjusting step of the outside diameter runout of lumped mass disk
No more than 0.005mm.
5. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 1 or 2,
It is characterized in that, turbine pump flexible rotor shaft system screw-down torque T in the step 90=7.5 × Major Diam.
6. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 5, special
Sign is, in the step 10 or step 11, turbine pump flexible rotor shaft system screw-down torque TkAdjusting step be not more than T0/
100。
7. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 1 or 2,
It is characterized in that, in the step 12, the rotor of turbine pump flex rotor is to moderate U0No more than the diameter of axle/600.
8. a kind of turbine pump flex rotor high-speed balancing quality consistency control method according to claim 7, special
Sign is, in the step 13 or step 14, the rotor of turbine pump flex rotor is to moderate UmAdjusting step be not more than
0.005mm。
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710221414.0A CN107084819B (en) | 2017-04-06 | 2017-04-06 | A kind of turbine pump flex rotor high-speed balancing quality consistency control method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710221414.0A CN107084819B (en) | 2017-04-06 | 2017-04-06 | A kind of turbine pump flex rotor high-speed balancing quality consistency control method |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107084819A CN107084819A (en) | 2017-08-22 |
| CN107084819B true CN107084819B (en) | 2019-01-11 |
Family
ID=59615210
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710221414.0A Active CN107084819B (en) | 2017-04-06 | 2017-04-06 | A kind of turbine pump flex rotor high-speed balancing quality consistency control method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107084819B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107883902B (en) * | 2017-10-25 | 2019-10-18 | 中国航发动力股份有限公司 | A kind of turbine rotor assembly jitter detection apparatus |
| CN109684767B (en) * | 2019-01-08 | 2020-09-15 | 北京理工大学 | Turbine pump inducer cavitation flow numerical prediction method based on low-temperature fluid |
| CN112709766A (en) * | 2021-01-18 | 2021-04-27 | 博格华纳联合传动系统有限公司 | Dynamic balance optimization method for high-pressure wet-type double clutches |
| CN114184321B (en) * | 2021-11-30 | 2024-04-05 | 珠海华粤传动科技有限公司 | Balance detection method, device and equipment for centrifugal pendulum vibration absorber |
| CN115541116B (en) * | 2022-11-24 | 2023-10-10 | 中国航发沈阳发动机研究所 | Control method for reducing rotation inertia excitation of turbine rotor |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1099945A2 (en) * | 1999-11-12 | 2001-05-16 | Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh | Procedure for balancing a shaft provided with vibration suppressing means |
| CN102374925A (en) * | 2011-09-22 | 2012-03-14 | 哈尔滨汽轮机厂有限责任公司 | High-speed dynamic balancing calibration method of gas turbine rotors with power of 254 MW |
| US9926786B2 (en) * | 2015-04-13 | 2018-03-27 | MTU Aero Engines AG | Method for joining at least two rotor elements of a turbomachine |
-
2017
- 2017-04-06 CN CN201710221414.0A patent/CN107084819B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1099945A2 (en) * | 1999-11-12 | 2001-05-16 | Mtu Motoren- Und Turbinen-Union Friedrichshafen Gmbh | Procedure for balancing a shaft provided with vibration suppressing means |
| CN102374925A (en) * | 2011-09-22 | 2012-03-14 | 哈尔滨汽轮机厂有限责任公司 | High-speed dynamic balancing calibration method of gas turbine rotors with power of 254 MW |
| US9926786B2 (en) * | 2015-04-13 | 2018-03-27 | MTU Aero Engines AG | Method for joining at least two rotor elements of a turbomachine |
Non-Patent Citations (3)
| Title |
|---|
| 浅析某型转子组合件动平衡技术;刘成乐;《机械制造》;20111231(第01期);全文 |
| 液体火箭发动机涡轮泵转子的新型动平衡方法研究;李斌等;《振动与冲击》;20111231(第06期);全文 |
| 燃气涡轮泵动平衡工艺优化;王春雷;《科技资讯》;20151231(第30期);全文 |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107084819A (en) | 2017-08-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN107084819B (en) | A kind of turbine pump flex rotor high-speed balancing quality consistency control method | |
| KR101657590B1 (en) | Reduction of turbocharger core unbalance with centering device | |
| EP1895164B1 (en) | Ball bearing turbocharger balancer | |
| WO2015120744A1 (en) | Aircraft engine rotor assembly method and device based on concentricity and perpendicularity measurement | |
| CN109991007B (en) | Containing test blade and containing test device | |
| CN107702854B (en) | A kind of high-speed balancing method for meeting rocket engine turbopump assembly and using | |
| CN110145541A (en) | A kind of magnetic suspension bearing rotor copsided operation control method based on phase stabilization | |
| CA1162458A (en) | Rotor for a hydroelectric machine | |
| CN106370411A (en) | High-temperature over-speed test change-over device for cantilever turbine disc | |
| WO2010111133A2 (en) | Reduction of turbocharger core unbalance with balance washer | |
| CN103452914A (en) | Assembly technique for reducing dynamic balance of rotor of turbocharger | |
| CN113051675B (en) | Mechanical checking method for influence of working temperature rise on dynamic characteristics of high-speed motor rotor | |
| CN105466691A (en) | Testing installation structure for rotor tip of gas compressor | |
| CN206161298U (en) | A high temperature overspeed test switching device for cantilever turbine disc | |
| CN105570187A (en) | Control method for dimensions of rotor tips of gas compressor | |
| CN205940874U (en) | Integrative turbopump rotor high -speed balancing of rocket engine dish axle drive coupling device | |
| CN202991240U (en) | High-rotary-speed and small-size pressure control device of turbine engine | |
| Kalmegh et al. | Dynamic balancing of centrifugal pump impeller | |
| CN210105926U (en) | Turbine disk, liquid rocket engine and liquid rocket | |
| CN109466730B (en) | Pitch adjusting device for pitch-adjusting propeller model and using method thereof | |
| CN201874684U (en) | Jaw chuck type speed regulator used in single cylinder diesel engine | |
| CN207421159U (en) | A kind of thrust disc structure of magnetic suspension rotor | |
| CN206425562U (en) | A kind of suitable high speed rotates the main shaft grasping system of turning | |
| CN117182643B (en) | Dynamic balance system for machine tool spindle | |
| CN108204896A (en) | A kind of simplification connection structure suitable for the experiment of circular arc end gear disc spins |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB03 | Change of inventor or designer information | ||
| CB03 | Change of inventor or designer information |
Inventor after: Dou Wei Inventor after: Li Ming Inventor after: Zhang Xiaona Inventor after: Shen Wenjin Inventor after: Tu Ting Inventor after: Jiang Wenshan Inventor after: Huang Kesong Inventor before: Liu Yang Inventor before: Dou Wei Inventor before: Jiang Xuqiang Inventor before: Yan Yulong Inventor before: Li Ming Inventor before: Zhang Zhaolei Inventor before: Yu Binkai Inventor before: Ye Xiaoming Inventor before: Xia Dexin |
|
| GR01 | Patent grant | ||
| GR01 | Patent grant |