Some standard content:
JB/T8557—1997
This standard is equivalent to the American Gear Manufacturers Association standard: AGMA515.02 "Balance Classification of Flexible Couplings", and the terms and measurement units are converted according to relevant Chinese standards. Appendix A of this standard is the appendix of the standard. This standard shall be implemented on January 1, 1998. This standard is proposed and managed by the National Technical Committee for Standardization of Machine Shafts and Accessories. The drafting units of this standard are: Mechanical Standardization Research Institute, Tongji University, 703 Institute of the Seventh Institute of China Shipbuilding Corporation, and Guizhou Metallurgical Transmission Machinery Factory. The main drafters of this standard are: Zhou Mingheng, Lian Xiangjiao, Chen Zhulin, Wang Zhaofu, and Cheng Guogang. 135
1 Scope
Mechanical Industry Standards of the People's Republic of China
Balance Classification of Flexible Couplings
JB/T8557 -1997
This standard specifies the balance classification of flexible couplings and is applicable to all types of flexible couplings and their parts. 2 Terminology
2.1 Balancing
Balancing is a method of checking the mass distribution of a rotor. If necessary, the mass distribution should be adjusted to limit the vibration of the bearing journal or the forces acting on the bearing. 2.2 Types of unbalanced conditions
2.2.1 Single-plane (force or static) unbalanced conditions If the center of gravity of an object is not on the axis of rotation, a single-plane unbalanced condition will occur (see Figure 1). In this case, no matter what the relative position of the object to the axis is, it is not in static equilibrium. 2.2.1.1 The angular position and amount of correction to be made in a single plane can be observed by placing the journal of the unbalanced object on two parallel horizontal bars or guides. The heavy side of the object always immediately turns below the axis. The correction method is to add a counterweight at the radial position of the symmetric point between the heavy side of the object and the center of rotation. On a static balancing machine, balancing in a single plane can be achieved without rotating the rotor. Centrifugal balancing machines are also often used to achieve balancing in a single plane.
2.2.2 Double-sided (torque, couple or dynamic) unbalanced state As shown in Figure 2, this unbalanced state occurs when there is a phase difference between the imbalances in the two planes. The phase is not necessarily 180°. The principal axis of inertia that was originally at the same position as the axis of rotation has deviated from the axis of rotation. In general, the two axes are skewed with respect to each other. When a rotating cylinder with an unbalanced torque, such as a coupling, is not restricted by the bearing, it will rotate around the principal axis of inertia, which is consistent with its geometric longitudinal axis. The torques (relative unbalanced forces) of equal magnitude and opposite direction with a phase difference of 180° are sometimes called couple unbalance. Figure 2 shows a double-sided unbalanced state The special case, because the center of gravity is on the axis of rotation, the part shown in the figure is in a single-plane equilibrium state.
Figure 1 Unbalance in a single plane
Approved by the Ministry of Machinery Industry of the People's Republic of China on April 15, 1997 136
1-Rotation axis; 2. Inertia axis
Figure 2 Unbalanced state in two planes
Implemented on January 1, 1998
2.3 Terminology of balance
2.3.1 Rigid rotation
JB/T 8557 - 1997
The rotor can be balanced and corrected in any two planes, and its unbalance will not significantly exceed the balance tolerance value (based on the axis) when it runs at any speed and under working conditions close to the support device. The rotor is a rigid rotor. It should be noted that flexible couplings usually consist of several parts, and the centering surfaces of these parts are offset and eccentric due to diameter errors. 2.3.2 Axis of rotation (rotation axis)
The axis of rotation is the line around which an object rotates. The straight line is determined by the journal, mating surface or other locating surface. 2.3.3 Offset of the principal axis of inertia
The offset of the principal axis of inertia relative to the axis of rotation. The two axes may be parallel in special cases, but in most cases they are not parallel, so the offsets in two commonly used balancing planes are often unequal. 2.3.4 Unbalance
Unbalance refers to the quantitative scale of the potential imbalance of the rotor (for a plane), without involving its angular position. 2.3.5 Potential imbalance Measure
Potential unbalance is the maximum unbalance that may exist in the coupling assembly after balancing (correction), disassembly and reassembly.
2.3.6 Balance level
The maximum value of unbalance is specified in Table 2. The value below Table 2 is the allowable coupling unbalance state. 2.3.7 Spindle
A shaft equipped with coupling parts or components for balancing. 2.3.8 Bushing
A shaft used to hold coupling parts or components together. 2.3.9 Spindle assembly
A spindle to which one or more sleeves are mounted. 2.3.10 Mounting surface
The surface of a spindle, sleeve, spindle assembly, on which a balancing tool, a part of a coupling, or an assembly is mounted. 2.3.11 Reference surface
The bearing surface on a part of a coupling or a coupling assembly, on which another part of a coupling is mounted. Some examples are given in Table 1.
Typical examples of coupling reference surfaces
3 responsibilities
Half coupling
Gear half coupling
Coupling parts
Inner gear ring with flange
Intermediate shaft with flange
Intermediate shaft with flange and shaft extension at one end
Intermediate sleeve with teeth at both ends
Intermediate sleeve with flange
Plate-shaped intermediate sleeve
Commonly used reference surfaces
Shaft hole, spigot diameter, bolt distribution circle diameter Shaft hole, wheel hub, tooth top circle diameter
Tooth root circle diameter, end ring diameter, spigot diameter, bolt distribution circle diameter Spigot diameter or bolt distribution circle diameter
Shaft extension diameter, spigot diameter, bolt distribution diameter Tooth head circle diameter
: Mouth diameter or bolt distribution circle diameter
: Mouth diameter or bolt distribution circle diameter
The liability of the coupling manufacturer is limited to the various guarantees made by the manufacturer as part of the sales contract. 137
JB/T 8557—1997
4 Potential unbalance factors that remain after correction (balanced) The potential unbalance factors of the corrected coupling assembly are explained in the following clauses. Chapter 6 gives the AGMA standard method for calculating the total effect of the above factors on the unbalance of the coupling, and Appendix A (standard appendix) is a calculation example. a) Balance correction tolerance;
b) Error of the balancing machine;
c) Unbalance of the balancing spindle assembly; d) Eccentricity of the mounting surface of the spindle assembly; e) Eccentricity of the coupling centering surface;
f) Clearance of the coupling centering surface;
g) Unbalance of accessories;
h) Other factors.
4.1 Balance correction tolerance
The balance correction tolerance is the maximum unbalance that does not require further correction. 4.2 Error of the balancing machine
The error of the balancing machine is mainly caused by the following factors: a) The sensitivity of all machine equipment except the drive machine; b) Only the error of the drive machine is considered.
4.3 Unbalance of balancing spindle assembly
The unbalance of balancing spindle assembly is the combined unbalance caused by all the parts on the spindle assembly, including spindle, bushing, half coupling, clamping device, key, set screw, nut and bolt, etc. 4.4 Eccentricity of spindle assembly mounting surface
The eccentricity refers to the eccentricity of the spindle assembly surface with the coupling assembly or parts installed relative to the axis of rotation of the balancing operation.
Eccentricity of coupling centering surface
This eccentricity refers to the eccentricity of any centering surface when assembling or reassembling after balancing operation. This eccentricity allows the axis of the center of gravity of another coupling part or assembly to have a corresponding radial displacement. This eccentricity is caused by the following factors: a) Due to the coaxiality of the part itself,
b) Due to the replacement of the centering surface after balancing 4.6 Clearance of coupling centering surface
The clearance of coupling centering surface refers to the corresponding radial displacement of the axis of the center of gravity of the coupling part or assembly when reinstalling after balancing operation. When the coupling is considered as an assembly for balancing, the potential radial displacement is equal to the entire radial clearance. When the coupling is balanced as a single part, the potential radial displacement is equal to half of the radial clearance. 4.7 Accessory Imbalance
Accessory Imbalance refers to the imbalance caused by all accessories of the coupling, including bolts, springs, washers, nuts, oil plugs, sealing rings, gaskets, keys, elastic retaining rings, positioning plates, thrust plates, locking nuts, etc. 4.8 Other factors
In addition to the above factors, any factors that affect the unbalance of the coupling must be considered. 5 Uncorrected potential unbalance factors of the coupling The factors that affect the potential unbalance of the coupling are described in the following items. Chapter 6 gives the AGMA standard method to calculate the total effect of these factors on the unbalance of the coupling. Appendix A is a calculation example. a) Uncorrected inherent unbalance of the coupling; 138
b) Eccentricity of the coupling centering surface;
c) Clearance of the coupling centering surface;
d) Unbalance of accessories;
e) Other factors,
5.1 Uncorrected inherent unbalance of the coupling
JB/T 8557 --1997
If the coupling as a whole or its parts are in an unbalanced state, one of the following two methods can be selected as the basis to determine the inherent unbalance caused by manufacturing errors:
a) Statistical analysis of the accumulated balance data of couplings manufactured according to the same design specifications; b) Theoretically calculate the maximum unbalance that may be produced according to the design specifications. 5.2 Eccentricity of the coupling centering surface
refers to the eccentricity of any centering surface that allows the center of gravity axis of another coupling assembly or part to undergo relative radial displacement. 5.3 Clearance of the coupling center surface
This clearance allows the axis of the center of gravity of the coupling parts or assemblies to have corresponding radial displacement. 5.4 Unbalance of accessories
Refers to the imbalance caused by all accessories of the coupling, including bolts, lock washers, nuts, oil plugs, seals, washers, keys, elastic retaining rings, positioning plates, thrust plates and lock nuts. 5.5 Other factors
In addition to the above factors, all factors that affect the imbalance of the coupling must be considered. 6 Coupling balance level
6.1 The balance level of any coupling assembly is determined by the square root of the sum of the squares of the maximum possible values of the eccentricity of the center of gravity between the main axis of inertia of the coupling and the axis of rotation. The unbalance specified in this standard is expressed in microns (μm). 6.2 The potential unbalance factors of coupling assemblies have been introduced in Chapter 4 and Chapter 5 respectively. The examples of determining the balance grade of various types of coupling assemblies and the various steps for calculating the balance are detailed in Appendix A. 6.3 The standard classification of coupling balance is shown in Table 2. The deviation of the main axis of inertia from the axis of rotation at the balance plane is expressed in maximum root mean square micrometers (μm), and its value is calculated according to the AGMA method in Appendix A. Table 2 Coupling balance standard grade
Coupling balance grade
Maximum deviation of the main axis of inertia on the balance plane (root mean square micrometer) μm
7 Coupling balance grade selection methodwww.bzxz.net
7.1 The coupling selector should select the appropriate coupling balance grade. Coupling balance grade
Maximum deviation of the inertia spindle on the balance plane (RMS micrometer) μm
7.2 Whether the unbalance of the coupling can meet the needs of any rotating system depends on the performance of each special connected machine, which is best determined by the manufacturer of the connected machine. 7.2.1 It is recommended that each machine manufacturer should also formulate an appropriate flexible coupling balance grade when providing its equipment. 7.3 If the appropriate coupling balance grade cannot be obtained from the machine manufacturer, Table 3 can be used as a reference guide for general selectors. 139
Selection area
(according to Figure 3)
JB/T 8557
Table 3 Typical values for coupling balance
Low system sensitivity to coupling imbalance
7.3.1 The recommended values listed in Table 3 are only typical selection examples and are not suitable for special systems or special machines. For some systems, if a coupling balance grade value lower than that recommended in Table 3 is used, the effect may be better. On the contrary, if some systems and machines are particularly sensitive to coupling imbalance, a balance grade value higher than that recommended in Table 3 should be used. 7.3.2 When using Table 3 as a guide for selecting the coupling balance grade, find the appropriate selection area from Figure 3 according to the net weight of the coupling and the maximum operating speed. The typical values of the coupling balance grade listed in Table 3 depend on the requirements of the system for the sensitivity of the coupling imbalance. 7.3.3 When determining the sensitivity of a mechanical transmission system to coupling imbalance, the following factors should be considered: a) Axial offset: If a machine has a long shaft extension or large flexibility, it is more sensitive to coupling imbalance; b) The relationship between the bearing load caused by the coupling mass and the total bearing load: If a machine uses light-loaded bearings or the bearing load is mainly caused by the cantilever load of the coupling, then this machine is more sensitive to coupling imbalance. Mechanical devices with cantilever rotors or cantilever loads are usually more sensitive to coupling imbalance; c) Rigidity of bearings, bearing seats and bases: Mechanical transmission systems with flexible bases or brackets for rotating parts are more sensitive to the unbalanced state of the coupling;
d) Natural frequency of the system: When the operation of the machine or mechanical transmission system is close to the resonant (resonant) frequency, it is more sensitive to the unbalanced state of the coupling;
e) Compactness of the machine: If the intermediate distance inside the mechanical transmission system is long (such as a coupling with a floating shaft), it is more sensitive to the unbalanced state of the coupling;
f) Other factors.
7.4 Example: Net weight of coupling, 68kg
Maximum operating speed: 7500r/min.
a) According to Figure 3, the appropriate coupling balance level selection area is "E\ area; b) According to Table 3, when a mechanical transmission system is expected to be moderately sensitive to the coupling imbalance, its typical selection area should be level 10 (if it is expected that the mechanical transmission system may have a lower or higher sensitivity to the coupling imbalance, level 9 and level 11 should be selected respectively).
JB/T8557—1997
Maximum operating speed, ×109r/min
Figure 3 Coupling balance selection area
Specific pressure exceeds the range of selection
guide
One year 50
A1 coupling balance Grade calculation examples
JB/T8557—1997
Appendix A
(Appendix to the standard)
AGMA coupling balance grade calculation
A1.1 This appendix uses numerical calculation as an example to determine the calculation method for the potential imbalance grade of various typical couplings. A1.1.1 The examples given in Table A1 include calibrated (balanced) and uncalibrated couplings. Table A1
Example catalogue
Types of couplings
Roller chain (double row) coupling
Diaphragm coupling
Elastic sleeve pin coupling
Elastic sleeve pin coupling
Snake Snake spring coupling
Snake spring coupling
Balance correction
Assembly
Assembly
Uncorrected
Single component
Uncorrected
Types of coupling
Marine intermediate shaft gear coupling
Marine intermediate shaft gear coupling
Intermediate sleeve gear coupling
Gear coupling
Gear coupling
Balance correction
Single component
Assembly
Single component
Assembly
Uncorrected||t t||A1.2 The values listed in the appendix, such as mass, geometry, tolerance and balance deviation, only illustrate the various factors that affect the imbalance of the coupling, and are not actual values. All examples in this appendix are based on a coupling with a net weight of 45 kg. The appropriate grade is selected according to the maximum eccentricity of the main axis of inertia, where greater than or less than 25 μm (see AGMA balance grade 10) represents a calibrated coupling; greater than or less than 50 μm represents an uncalibrated coupling (see AGMA balance grade 9). A1.3 The eccentricity measured in all examples includes a correction factor, which reflects the sensitivity of the dry meter and is calculated according to formula (A1): (i+R)
× 105
Where: e-actual eccentricity, μm;
percentage reading of a micrometer, um;
i—minimum scale of the micrometer, um.
A1.4 In all examples, the imbalance caused by the difference in mass of the accessories is estimated according to formula (A2): V AWD × 2
-actual imbalance of each accessory, g·mm; where. V
AW is the maximum mass deviation of the accessory, g;
D is the radius of the bolt distribution circle, mm.
...Al)
....(A2)
Example 1: Balancing calculation of roller chain (double row) coupling. JB/T 8557 -1997
1-Cover; 2-Chain; 3---Half coupling
Figure A1 Schematic diagram of roller chain (double row) coupling Coupling geometry and parameters
a) Mass
1) Total mass of coupling
2) Mass of coupling parts
①Chain
②Cover
3) Mass of balancing tool
①Spindle
②Sleeve
b) Balancing correction tolerance
c) Error of balancing test machine
1) Sensitivity||t t||2) Error in the driving device
d) Unbalance of the balancing spindle assembly
e) Scale of the micrometer
f) Eccentricity of the mounting surface of the spindle assembly
1) Runout of the sleeve mounting surface to the spindle axis2) Clearance between the spindle and the sleeve
3) Runout of the sleeve aperture to its mounting surface4) Clearance between the sleeve mounting surface and the sleeve hole
g) Eccentricity of the coupling centering surface
Assuming that all parts are marked with unbalance, the balancing operation involves compensating for these eccentricities (imbalance). h) Clearance of the coupling centering surface
1) Clearance from the chain pitch line to the sprocket pitch diameter
2) Clearance between the outer diameter of the sleeve and the housing
i) Unbalance of accessories
1) Unbalance of each accessory
2) Bolt distribution circle diameter
Calculation of the unbalance of each correction surface
a) Balance correction tolerance
45×10×2.54×10-3
b) Error of the balancing test machine
1) Sensitivity
51.7×10×0. 25×10*3
2) Error of the driving device
51.7×10×0.25×10-3
c) Unbalance of the balancing spindle assembly
JB/T 8557—1997
Spindle assembly
(4.5×10*+0.9×10+0.9X10)×0. 25×10-3d) Eccentricity of the mounting surface of the spindle assembly
1) Spindle runout
47×10×(25.4×10*±12.7×10-)2
2) Clearance between sleeve and spindle
47×10°×1.27×10-
3) Runout of sleeve aperture to its outer diameter
45×10×1.27×10 *
4) Clearance between the outer diameter of the sleeve and the sleeve hole
45×10°×25.4×10-
e) Eccentricity of the coupling centering surface
(See Table 2 for balance grade 10)
f) Clearance of the coupling centering surface
1) Clearance from the chain pitch line to the sprocket pitch diameter
×50.8×10~3
2) Clearance between the outer diameter of the half coupling and the housing 1.8×103
X50.8X10-3
g) Unbalance of accessories
Fasteners (error of each part)
1-4X162 ×
h) Others
Total:
Root mean square value of potential unbalance: V157788-397.2g·mm397.2×103
Root mean square value offset from the principal axis of inertia: 45×103/2
The balance grade is coupling balance grade 10. 144
(g·mm)2
Not applicable
157788
Example 2: Diaphragm coupling balance calculation.
Geometric shape and parameters of coupling
a) Mass
1) Total mass of coupling
2) Mass of coupling parts
①D half coupling 2×12.2
②Intermediate shaft
③Diaphragm set 2×3.6
①Accessory 2×2
3) Mass of balancing tool
①Spindle
②Sleeve 2×2.7
b) Balancing correction tolerance
c) Error of balancing test machine
1) Sensitivity
2) Error of driving device
JB/T 8557 -- 1997
1 Diaphragm group; 2 Intermediate shaft; 3 Half coupling
Figure A2 Schematic diagram of diaphragm coupling
d) Unbalance of balancing spindle assembly
e) Scale of micrometer
f) Eccentricity of spindle assembly mounting surface
1) Runout of sleeve mounting surface with respect to spindle axis 2) Runout of sleeve aperture with respect to its mounting surface 3) Clearance between sleeve mounting surface and sleeve hole
g) Eccentricity of coupling centering surface
7.2 g＇μm
Assuming that all parts are marked with unbalance, the balancing operation means compensating for these eccentricities (unbalance). h) Clearance of the centering surface of the coupling
Internal clearance
i) Unbalance of accessories
Accessories (error of each part)
Calculate the unbalance amount of each correction surface
a) Balance correction tolerance
45×103
×5×10-3
b) Error of the balancing test machine
1) Sensitivity
55.3×103||tt ||X25.4×10-5
2) When the error of the driving device = 0.28g
c) Unbalance of the balanced spindle assembly
1) Spindle
2)) Bushing
3) Spindle assembly
9.9×10×2.54×10-4
d) Eccentricity of the mounting surface of the spindle assembly
1) Spindle runout
JB/T 8557
50.8×103
X(12.7X10-3+12. 7X10-*
2) Clearance between sleeve and sleeve hole
45×10°×10.1×10-3
3) Runout of sleeve mounting surface
45×10×(12.7×10-+12.7×10)2
e) Eccentricity of coupling centering surface
(See Table 2 for balance grade 10)
f) Clearance of coupling centering surface
1) Internal clearance
(9.5×103
+3.6×10*+2×103)×31.7×10~3g）Unbalance of accessories
42.5×86.6X
h）Others
Total:
Root mean square value of potential unbalance: V346905=589g·mm589103
Offset of root mean square value to the main axis of inertia: 2=26.2 μm
:45×10*/2
Balance grade is coupling balance grade 10.146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
34690545×10*/2
Balance grade is coupling balance grade 10. 146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
34690545×10*/2
Balance grade is coupling balance grade 10. 146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
34690527×10 *
4) Clearance between the outer diameter of the sleeve and the sleeve hole
45×10°×25.4×10-
e) Eccentricity of the coupling centering surface
(See Table 2 for balance grade 10)
f) Clearance of the coupling centering surface
1) Clearance from the chain pitch line to the sprocket pitch diameter
×50.8×10~3
2) Clearance between the outer diameter of the half coupling and the housing1.8×103
X50.8X10-3
g) Unbalance of accessories
Fasteners (error of each part)
1-4X162 ×
h) Others
Total:
Root mean square value of potential unbalance: V157788-397.2g·mm397.2×103
Root mean square value offset from the principal axis of inertia: 45×103/2
The balance grade is coupling balance grade 10. 144
(g·mm)2
Not applicable
157788
Example 2: Diaphragm coupling balance calculation.
Geometric shape and parameters of coupling
a) Mass
1) Total mass of coupling
2) Mass of coupling parts
①D half coupling 2×12.2
②Intermediate shaft
③Diaphragm set 2×3.6
①Accessory 2×2
3) Mass of balancing tool
①Spindle
②Sleeve 2×2.7
b) Balancing correction tolerance
c) Error of balancing test machine
1) Sensitivity
2) Error of driving device
JB/T 8557 -- 1997
1 Diaphragm group; 2 Intermediate shaft; 3 Half coupling
Figure A2 Schematic diagram of diaphragm coupling
d) Unbalance of balancing spindle assembly
e) Scale of micrometer
f) Eccentricity of spindle assembly mounting surface
1) Runout of sleeve mounting surface with respect to spindle axis 2) Runout of sleeve aperture with respect to its mounting surface 3) Clearance between sleeve mounting surface and sleeve hole
g) Eccentricity of coupling centering surface
7.2 g＇μm
Assuming that all parts are marked with unbalance, the balancing operation means compensating for these eccentricities (unbalance). h) Clearance of the centering surface of the coupling
Internal clearance
i) Unbalance of accessories
Accessories (error of each part)
Calculate the unbalance amount of each correction surface
a) Balance correction tolerance
45×103
×5×10-3
b) Error of the balancing test machine
1) Sensitivity
55.3×103||tt ||X25.4×10-5
2) When the error of the driving device = 0.28g
c) Unbalance of the balanced spindle assembly
1) Spindle
2)) Bushing
3) Spindle assembly
9.9×10×2.54×10-4
d) Eccentricity of the mounting surface of the spindle assembly
1) Spindle runout
JB/T 8557
50.8×103
X(12.7X10-3+12. 7X10-*
2) Clearance between sleeve and sleeve hole
45×10°×10.1×10-3
3) Runout of sleeve mounting surface
45×10×(12.7×10-+12.7×10)2
e) Eccentricity of coupling centering surface
(See Table 2 for balance grade 10)
f) Clearance of coupling centering surface
1) Internal clearance
(9.5×103
+3.6×10*+2×103)×31.7×10~3g）Unbalance of accessories
42.5×86.6X
h）Others
Total:
Root mean square value of potential unbalance: V346905=589g·mm589103
Offset of root mean square value to the main axis of inertia: 2=26.2 μm
:45×10*/2
Balance grade is coupling balance grade 10.146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
34690527×10 *
4) Clearance between the outer diameter of the sleeve and the sleeve hole
45×10°×25.4×10-
e) Eccentricity of the coupling centering surface
(See Table 2 for balance grade 10)
f) Clearance of the coupling centering surface
1) Clearance from the chain pitch line to the sprocket pitch diameter
×50.8×10~3
2) Clearance between the outer diameter of the half coupling and the housing1.8×103
X50.8X10-3
g) Unbalance of accessories
Fasteners (error of each part)
1-4X162 ×
h) Others
Total:
Root mean square value of potential unbalance: V157788-397.2g·mm397.2×103
Root mean square value offset from the principal axis of inertia: 45×103/2
The balance grade is coupling balance grade 10. 144
(g·mm)2
Not applicable
157788
Example 2: Diaphragm coupling balance calculation.
Geometric shape and parameters of coupling
a) Mass
1) Total mass of coupling
2) Mass of coupling parts
①D half coupling 2×12.2
②Intermediate shaft
③Diaphragm set 2×3.6
①Accessory 2×2
3) Mass of balancing tool
①Spindle
②Sleeve 2×2.7
b) Balancing correction tolerance
c) Error of balancing test machine
1) Sensitivity
2) Error of driving device
JB/T 8557 -- 1997
1 Diaphragm group; 2 Intermediate shaft; 3 Half coupling
Figure A2 Schematic diagram of diaphragm coupling
d) Unbalance of balancing spindle assembly
e) Scale of micrometer
f) Eccentricity of spindle assembly mounting surface
1) Runout of sleeve mounting surface with respect to spindle axis 2) Runout of sleeve aperture with respect to its mounting surface 3) Clearance between sleeve mounting surface and sleeve hole
g) Eccentricity of coupling centering surface
7.2 g＇μm
Assuming that all parts are marked with unbalance, the balancing operation means compensating for these eccentricities (unbalance). h) Clearance of the centering surface of the coupling
Internal clearance
i) Unbalance of accessories
Accessories (error of each part)
Calculate the unbalance amount of each correction surface
a) Balance correction tolerance
45×103
×5×10-3
b) Error of the balancing test machine
1) Sensitivity
55.3×103||tt ||X25.4×10-5
2) When the error of the driving device = 0.28g
c) Unbalance of the balanced spindle assembly
1) Spindle
2)) Bushing
3) Spindle assembly
9.9×10×2.54×10-4
d) Eccentricity of the mounting surface of the spindle assembly
1) Spindle runout
JB/T 8557
50.8×103
X(12.7X10-3+12. 7X10-*
2) Clearance between sleeve and sleeve hole
45×10°×10.1×10-3
3) Runout of sleeve mounting surface
45×10×(12.7×10-+12.7×10)2
e) Eccentricity of coupling centering surface
(See Table 2 for balance grade 10)
f) Clearance of coupling centering surface
1) Internal clearance
(9.5×103
+3.6×10*+2×103)×31.7×10~3g）Unbalance of accessories
42.5×86.6X
h）Others
Total:
Root mean square value of potential unbalance: V346905=589g·mm589103
Offset of root mean square value to the main axis of inertia: 2=26.2 μm
:45×10*/2
Balance grade is coupling balance grade 10.146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
3469057×10~3g) Unbalance of accessories
42.5×86.6X
h) Others
Total:
Root mean square value of potential unbalance: V346905=589g·mm589103
Offset of the root mean square value to the principal axis of inertia: 2=26.2 μm
:45×10*/2
Balance grade is coupling balance grade 10.146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
3469057×10~3g) Unbalance of accessories
42.5×86.6X
h) Others
Total:
Root mean square value of potential unbalance: V346905=589g·mm589103
Offset of the root mean square value to the principal axis of inertia: 2=26.2 μm
:45×10*/2
Balance grade is coupling balance grade 10.146
(g·mm)2
Not applicable
Not applicable
103684
107584
Not applicable
346905
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