Some standard content:
Mechanical Industry Standard of the People's Republic of China
JB/T 6138-1992
AMN Internal Friction Safety Coupling
Published on June 9, 1992
Implementation by the Ministry of Machinery and Electronics Industry of the People's Republic of China on January 1, 1993
Mechanical Industry Standard of the People's Republic of China
AMN Internal Friction Safety Coupling
Subject Content and Scope of Application
JB/T 6138-1992
This standard specifies the type, structural dimensions, technical requirements, test methods and inspection rules of AMN internal friction safety coupling (hereinafter referred to as coupling).
This standard is applicable to the transmission shaft system connecting two coaxial lines. It plays the role of limiting torque and overload protection. The sliding torque is 10~6300Nm.
Referenced standards
GB3507
GB3852
GB3931
GB4879
GB9439
GB9440
GB11352
GB12458
JB3063
Technical conditions for cold-rolled cylindrical helical compression springs Nominal torque of mechanical couplings Series
Shaft hole and keyway type and size of coupling
Terminology of mechanical coupling
Rust-proof packaging
Gray cast iron parts
Mallet cast iron parts
Casting carbon steel parts for general engineering
Classification of mechanical coupling
Friction materials of powder metallurgy
Heat storage capacity: The heat stored in the coupling due to friction during the working process. Sliding torque: The torque value transmitted by the coupling at the moment when the driving and driven ends begin to slide relative to each other. Maximum sliding torque: The allowable value of the sliding torque of the coupling. 4 Type, basic parameters and dimensions
4.1 Type, basic parameters and dimensions shall comply with the provisions of Figure 1 and Table 1. Standard
AMN1-AMN4
1 Half coupling I;
Approved by the Ministry of Machinery and Electronics Industry on 1992-06-09 Figure 1
2 A friction plate;
AMN5-AMN6
3 An intermediate ring; 4 A compression spring; 5 Half coupling 1993-01-01 implementation
Clearing torque
Shaft hole diameter
20,22,24
30,32,35,38
40,42,45.48
40,42,45,48
60,63,65,70,71,75
60,63,65, 70
80,85,90
70,71,75
80,85,90,95
100,110,120,125
100,110,120.125
130.140,150
Shaft hole length
Note: The sliding torque value is based on the series value specified in GB3507. The error of the dynamic torque shall not exceed the value of the sliding torque of ±6%. JB/T6138-1992
The type and size of the shaft hole and keyway shall be in accordance with the relevant provisions of GB3852 4.2
The shaft hole type shall comply with the provisions of Y type and J type, and can be combined arbitrarily. The keyway type shall comply with the provisions of A type.
3 Model and marking
4.3.1 Model representation method
Marking example
Specification code
Coupling code
Example 1AMN2 coupling, sliding torque is 125Nm
Driving end: Y-type shaft hole, d,=48mm, L=112mmDriven end: J, type shaft hole, dz=40mm, L=84mmMarked as: AMN2 coupling
5 Technical requirements
48×112
J,40×84
JB/T6138—92
180 **
5.1 The coupling shall comply with the requirements of this standard and be manufactured in accordance with the drawings and design documents approved by the prescribed procedures. 5.2 Friction lining
Soft moment of inertia
Coupling
Half coupling!
JB/T 6138-1992
JB/T6138-1992
4.2 The type and size of the shaft hole and keyway shall comply with the relevant provisions of GB3852. The shaft hole type shall comply with the provisions of Y type and J type, and can be combined arbitrarily. The keyway type shall comply with the provisions of A type.
4.3 Model and marking
4.3.1 Model indication method
4.3.2 Marking example
Specification codeWww.bzxZ.net
Coupling code
Example 1AMN2 coupling, sliding torque is 125Nm
Driving end: Y-type shaft hole, d,=48mm, L=112mmDriven end: J, type shaft hole, dz=40mm, L=84mm48×112
Marked as: AMN2 coupling
J,40×84
5 Technical requirements
JB/T6138—92
5.1 The coupling shall comply with the requirements of this standard and be manufactured in accordance with the drawings and design documents approved by the prescribed procedures. 5.2 Friction lining
Friction lining is not allowed to have cracks, scars, unevenness, warping, twisting and other defects that affect its use. The physical and mechanical properties of friction materials shall comply with the provisions of Table 2. Table 2
Friction coefficient u
5.3 Compression spring
Wear rate
10*cm/Nm
Compression spring shall comply with the relevant provisions of GB1239. Hardness
Tensile strength
Compression spring is made of spring steel with mechanical properties not less than 65S12MnWA, and the manufacturing accuracy adopts first-class accuracy. 5.4 The intermediate ring is made of material with mechanical properties not less than KTZ55004 specified in GB9440. 5.5 Half coupling I is made of HT250 specified in GB9439. Compressive strength
5.6 Half coupling II of AMN1~AMN4 is made of material with mechanical properties not lower than KTZ55004 specified in GB9440. Half coupling II of AMN5~AMN6 is made of material with mechanical properties not lower than ZG270-500 specified in GB11352. 5.7 Installation
5.7.1 The installation accuracy of the coupling shall comply with the provisions of Figure 2 and Table 3. 3
JB/T6138-1992
During installation, the working surface of the friction pair should not have lubricating oil, grease or other substances that affect the use. 5.7.2
5.8 If the purchaser has requirements for the dynamic balance of the coupling, the supply and demand parties shall agree in the order agreement. 6 Test method
6.1 Performance test
Check whether the coupling is manufactured according to the specified drawings and design documents. 6.1.1
6.1.2 Under the condition that the temperature rise does not exceed 100℃, the friction pair shall be run-in until the contact area reaches more than 80%. mm
6.1.3 Fix the driven end of the coupling, gradually load the driving end, and measure the static friction torque when relative rotation occurs between the driven end and the driving end. The number of measurements shall be no less than 3 times, and the arithmetic mean shall be taken. 6.1.4 Make the speed of the coupling reach the test speed, increase the load torque on the driven end side, and measure the friction torque when relative rotation occurs between the driven end and the driving end. Then, reduce the load torque on the driven end, and measure the friction torque when the synchronous speed is restored between the driven end and the driving end. The number of measurements shall be no less than 5 times, and the arithmetic mean shall be taken. 6.2 Friction lining
6.2.1 Determination of static friction coefficient
6.2.1.1 This method is to load until slipping under specified conditions and measure the static friction coefficient μJ. 4
JB/T6138-1992
6.2.1.2 The specimen shall comply with the provisions of Article 2.5.2.2 of JB3063. The material of the counterpart shall be 250HT as specified in GB9439. 6.2.1.3 Test method and calculation
The specimen and counterpart shall be respectively installed on the MM-1000 friction testing machine for running-in. Specification: specific pressure p≤50N/cm2;
Speed: n=200~500r/min;
Requirement: When the contact area between the specimen and the counterpart reaches more than 80%, the running-in is considered to be completed. b. Test operation
Start the testing machine and set the spindle speed n to 70r/min. After rotating for 30s, apply a pressure of 60N/cm2. After stopping for 5s, continue to slowly load the spindle until it slips. Repeat 5 times and take the average torque. c.Calculation method
Static friction coefficient μ is calculated according to formula (1):
-Maximum torque when the friction pair slips, Nm;
Where: M
Total pressure acting on the end surface of the friction pair, N; R—Average radius of the inner and outer circles of the specimen, m. (1)
6.2.2 The determination of dynamic friction coefficient shall be carried out in accordance with the provisions of 2.5.1 to 2.5.3 of JB3063, and the mating material shall be in accordance with the provisions of 6.2.1.2 of this standard.
6.2.3 Determination of wear rate
6.2.3.1 The test method shall be in accordance with the provisions of 2.5.1 of JB3063. 6.2.3.2 Calculation method
The wear rate is calculated according to formula (2):
Wear rate, cm/Nm;
Where: V
-Cumulative linear wear, cm;
-Total average friction torque during the test, N
NTotal number of revolutions during the test.
6.3 Compression spring
Compression springs are not allowed to have permanent deformation after being pressed at 250℃ for 12 hours. 7 Inspection rules
7.1 All couplings produced in accordance with this standard must be inspected before leaving the factory. The inspection items shall be carried out in accordance with 6.1.2-6.1.3. (2)
7.2 Factory couplings are not subject to type inspection. Type inspection is only carried out before new products are put into production. When the formula or process of the friction lining is changed, type inspection must be carried out. Type inspection items shall be carried out in accordance with the provisions of 6.1~6.3. 8 Marking, packaging, storage
8.1 Marking
The marking of the coupling should include the following: a. Manufacturer name;
b. Product name;
Product model;
Date of manufacture.
JB/T6138-1992
After the coupling leaves the factory, it should be cleaned and packed for rust prevention according to the provisions of GB4879. The following documents should be attached to the packing box:
Product certificate;
b. Product instruction manual;
Packing list;
List of accessories.
8.3 Storage
The coupling should be stored in a dry and ventilated environment to avoid oil, water contamination and acid and alkali corrosion. 6
A1 Selection principles
JB/T6138—1992
Appendix A
Selection instructions for coupling
(reference)
The sliding torque shall not be greater than the maximum sliding torque of the coupling. a.
b. The heat storage capacity of the coupling shall not exceed the heat storage capacity at the maximum allowable temperature rise of the coupling (4Tx=250℃). The working temperature of the coupling shall not be greater than 250℃. c.
d. It is not suitable for occasions with frequent forward and reverse rotation. 2 Used for motor or machine starting
The sliding torque can generally be determined based on the principle of exceeding the working torque by 25%, which can be calculated by the following formula: Th=KT.
T=9549×
Where: Th
The sliding torque of the coupling, Nm;
The coefficient is generally taken as 1.25, and can also be determined separately according to actual needs: 7
-working torque, Nm;
The maximum power transmitted, kW;
Speed, r/min.
Starting time calculation formula:
J(nz-n)
to=0.1047x
Where: to
Starting time, s:
Converted to the moment of inertia on the coupling (including the passive side of the coupling), kgm2; the working speed of the active side of the coupling, r/min; the starting speed of the driven side of the coupling, generally n,=0, r/min; converted to the load torque at the time of starting on the coupling, Nm.
Calculation formula for heat generation during starting:
Where: 0
Q=5.5x10-(nz -n,)2
(1-T/T)
Heat generation during starting, kJ.
A2.4 When the half coupling I does not rotate, the relationship between the heat storage Qx and the cooling time t of the couplings of various specifications at different temperature rises △T is shown in Figure A1. When the half coupling I rotates, the correct cooling time is tL found in Figure A1, divided by the heat dissipation coefficient f found in Figure A2.
5 When the half coupling I rotates, the relationship between the speed n and the heat dissipation coefficient f is shown in Figure A2. A2.6
5 When the half coupling I does not rotate, the relationship between the temperature rise △T and the heat dissipation 9o of the couplings of various specifications is shown in Figure A3. 7
JB/T6138-1992
When the half coupling I rotates, the heat dissipation g is 9o multiplied by the heat dissipation coefficient f: q=qof
1250°0
ST..-250°C
130°c
100°℃
20003000
AMN4 AMN5
A2.7 Calculation for selection
JB/T 6138-1992
For the convenience of verification, the coupling is divided into three categories according to the working conditions. A2.7.1 One-time start or repeated start in a short period of 200
In this case, only the total heat generated by friction is checked to see if the temperature rise exceeds the allowable temperature rise. In addition, the start interval time should also be controlled. Example 1
Given: J=9.5kgm, nz=950r/min, n,=0, Tp=25Nm, T=125N
Solution: According to formula (A4), the heat generated during one start-up can be calculated: Q=5.5x10-x (nz -n,)2
(1T/T)
=5.5x10 9.5×(950-0)
(1-25/125)
=58.9(kJ)
Select AMN2 coupling:
From Figure A1, it can be found that when △T=250℃, Qx=355.8kJm
Since 60=6×58.9=353.4(kJ)
T=9549×
Wherein: Th
sliding torque of coupling, Nm;
coefficient, generally 1.25, can also be determined according to actual needs: 7
-working torque, Nm;
maximum power transmitted, kW;
speed, r/min.
starting time calculation formula:
J(nz-n)
to=0.1047x
Wherein: to
starting time, s:
converted to the moment of inertia on the coupling (including the passive side of the coupling), kgm2; working speed on the active side of the coupling, r/min; starting speed on the driven side of the coupling, generally n,=0, r/min; converted to the load torque at the start of the coupling, Nm.
Calculation formula for heat generation during the starting process:
Where: 0
Q=5.5x10-(nz -n,)2
(1-T/T)
Heat generation during the starting process, kJ.
A2.4When the half-coupling I does not rotate, the relationship between the heat storage Qx and the cooling time t of couplings of various specifications at different temperature rises △T is shown in Figure A1. When the half-coupling I rotates, the correct cooling time is tL found in Figure A1, divided by the heat dissipation coefficient f found in Figure A2.
5When the half-coupling I rotates, the relationship between the speed n and the heat dissipation coefficient f is shown in Figure A2. A2.6
5When the half-coupling I does not rotate, the relationship between the temperature rise △T and the heat dissipation 9o of couplings of various specifications is shown in Figure A3. 7
JB/T6138-1992
When the half coupling I rotates, the heat dissipation g is 9o multiplied by the heat dissipation coefficient f: q=qof
1250°0
ST..-250°C
130°c
100°℃
20003000
AMN4 AMN5
A2.7 Calculation for selection
JB/T 6138-1992
For the convenience of verification, the coupling is divided into three categories according to the working conditions. A2.7.1 One-time start or repeated start in a short period of 200
In this case, only the total heat generated by friction is checked to see if the temperature rise exceeds the allowable temperature rise. In addition, the start interval time should also be controlled. Example 1
Given: J=9.5kgm, nz=950r/min, n,=0, Tp=25Nm, T=125N
Solution: According to formula (A4), the heat generated during one start-up can be calculated: Q=5.5x10-x (nz -n,)2
(1T/T)
=5.5x10 9.5×(950-0)
(1-25/125)
=58.9(kJ)
Select AMN2 coupling:
From Figure A1, it can be found that when △T=250℃, Qx=355.8kJm
Since 60=6×58.9=353.4(kJ)
T=9549×
Wherein: Th
sliding torque of coupling, Nm;
coefficient, generally 1.25, can also be determined according to actual needs: 7
-working torque, Nm;
maximum power transmitted, kW;
speed, r/min.
starting time calculation formula:
J(nz-n)
to=0.1047x
Wherein: to
starting time, s:
converted to the moment of inertia on the coupling (including the passive side of the coupling), kgm2; working speed on the active side of the coupling, r/min; starting speed on the driven side of the coupling, generally n,=0, r/min; converted to the load torque at the start of the coupling, Nm.
Calculation formula for heat generation during the starting process:
Where: 0
Q=5.5x10-(nz -n,)2
(1-T/T)
Heat generation during the starting process, kJ.
A2.4When the half-coupling I does not rotate, the relationship between the heat storage Qx and the cooling time t of couplings of various specifications at different temperature rises △T is shown in Figure A1. When the half-coupling I rotates, the correct cooling time is tL found in Figure A1, divided by the heat dissipation coefficient f found in Figure A2.
5When the half-coupling I rotates, the relationship between the speed n and the heat dissipation coefficient f is shown in Figure A2. A2.6
5When the half-coupling I does not rotate, the relationship between the temperature rise △T and the heat dissipation 9o of couplings of various specifications is shown in Figure A3. 7
JB/T6138-1992
When the half coupling I rotates, the heat dissipation g is 9o multiplied by the heat dissipation coefficient f: q=qof
1250°0
ST..-250°C
130°c
100°℃
20003000
AMN4 AMN5
A2.7 Calculation for selection
JB/T 6138-1992
For the convenience of verification, the coupling is divided into three categories according to the working conditions. A2.7.1 One-time start or repeated start in a short period of 200
In this case, only the total heat generated by friction is checked to see if the temperature rise exceeds the allowable temperature rise. In addition, the start interval time should also be controlled. Example 1
Given: J=9.5kgm, nz=950r/min, n,=0, Tp=25Nm, T=125N
Solution: According to formula (A4), the heat generated during one start-up can be calculated: Q=5.5x10-x (nz -n,)2
(1T/T)
=5.5x10 9.5×(950-0)
(1-25/125)
=58.9(kJ)
Select AMN2 coupling:
From Figure A1, it can be found that when △T=250℃, Qx=355.8kJm
Since 60=6×58.9=353.4(kJ)
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