I. Main parameters
Anchor chain diameter: 34 (AM2).
Workload: 49.13kN
Overload pull: 73.7kN
Support load: 294.75 kN
Anchor speed: 12.9m/min
Anchor depth: ≤82.5m
Motor specifications: Type: JZ2-H51-4/8/16
Power: 16/16/11kW
Speed: 1400/665
Duty: min10/30/5
Power source: AC360V;

II.Overall calculation
1. Workload calculation
2. Overload pull calculation
3. Holding load calculation
4. Transmission ratio calculation
Big gear
Worm Gear
5. Speed calculation
6. Efficiency calculation
There are several factors that affect the efficiency of the anchor windlass
Worm gear efficiency
Open Gear drive rate
Chain cable lifter engagement rate
Sliding bearing carrying efficiency
Dog-type clutch meshing efficiency
Coupling efficiency
windlass efficiency:
7.Power calculation
When workload,
Pick motor model: -H51-4/8/16 Power: 16/16/11kW
8.Torque calculation of each driven shaft
- When workload
Gypsy axle
Worm gear axle
2)The torque of each shaft when the motor is blocked
When the motor is blocked
That is: when the motor has blocked the torque that each axis is subjected to increase to 2.35 times on the basis of workload stress on each axis

torque
III. Worm gear box selection
Select the normal cylindrical worm reducer according to the
standard
At workload time, the worm shaft torque is .
Check the load-bearing capacity table, the transmission ratio =11.67 ,center distance is 250
therefore selected WD250 gearbox (worm shaft and worm shaft need to be custom-made)
IV. Open gear strength check
m=10 \#45\n 220~250HB
m=10 ZG310-570 220~250HB
=15
=10
Small gear Big gear
1. Root stress calculation
When working, Pinion shaft torque
Circumference force
Usage factor:
Dynamic load factor:
Toothed load distribution factor:
Interdental load distribution factor:
Composite profile coefficient:
Coincidentity and helix angle coefficient:
If your coefficients are different, the school check will need to be provided
Root stress
2.Allowed root stress calculation
The basic value of bending fatigue strength of the gear material
The life factor calculated for bend strength
Relative root fillet sensitivity coefficient
Relative surface condition coefficient
The dimensional factor for bend strength calculation
The minimum safety factor for bending strength
Allow root stress
3. Calculated safety factor of bending strength
4 Stress core when the motor is blocked
When the motor is blocked, the stress is 2.35 times that of the workload
When the motor is blocked, the small gear calculates the stress
The large gear calculates the stress
V. Strength check of shaft
- Worm Gear Axle
Worm Gear Axle by the reduction box manufacturers, manufacturers in accordance with national standards requirements for manufacturing, to ensure the strength of the shaft requirements, the outstretched end, and pinion link, suspension wall (cantilever) arrangement, in the face of torque at the same time, bear the radial force of the big gear, the current school nuclear worm axle outstretched the end root to withstand the bending stress.
Shaft material 45 steel, tuning treatment HB217 ~255
The worm gear axle outstretched end is made by the product sample

1. When the workload is in, the pinion shaft torque
T=2232.5(Nm) =2232500(Nm)
Circumference force:
The root is subjected to bending moment
The hazardous cross-sectional stress is calculated by bending synthes
The stress of the promised use
The stress is much greater than the calculated stress , and the intensity is checked when overloaded.
2 Gypsy strength core
Shaft material Tuning treatment
2.1 a fatiguestrength core


When workloads,
Horizontal force at the cable wheel
Vertical force at the gypsy
At the time of the workload, the gypsy torque \left( Nm \right)
Large gear circumference force (i.e. vertical force)
Large gear radial force (i.e. horizontal force)
2.1.1 When C-points are subject to workload, ask for A-point and B-point horizontal forces
The level at which point C is forced is tried

Ask for A-point force
Find the B-point force
2.1.2 When C-points are subject to workload, seek vertical force C-Point at points A and B
The vertical force at point C is

Vertical force C-point
2.1.3 When C-points are under workload, seek A-point and B-points
2.1.4 When theC point is under the workload, find the C,E point bend moment
2.1.5 When the D-point is under the workload, the A-point and B-point levels are forced
Levels are sought

2.1.6 When D-points are under the workload, seek vertical force at points A and B
Vertically sought

2.1.7 When you are under workload at point D, ask for A and B points to work together
2.1.8 When you are under workload at point D, ask for A and B points to work together
2.1.9 The dangerous cross-section stress is calculated by bending moment synthesis
Comparing and
, it can be seen that when
point is forced,the maximum bending moment is
Nm, at which the stress of the axis can be calculated. As can be seen from the pre-calculation, the torque of the shaft is
Nm when the workload is loaded
Calculate the stress of the axis
It is safe to use
2.1.9.2 The core of the shaft strength when the motor is blocked
According to the previous calculation, the stress of the shaft is enlarged times when the motor is blocked.
When the motor is blocked, the shaft is stressed
2.1.9.3 When under support load, the strength of the axis is checked
The spindle only bears the support load pull and the braking force is stationary, only the bending moment
The gypsy’s support load pull is 294750 N
Horizontal force at the gypsy
Vertical force at the gypsy
Brake horizontal force
Brake horizontal force
Brake vertical force