## 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: JZ_{2}-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