SatNOGS Rotator v3

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SatNOGS Rotator v3
SatNOGS Rotator v3
Rotator Information
Type: Az/El
Cost: ~200 USD
Release Information
Status: Beta
Latest Release: Torx Flathead (v3.0.1)
Repository: [1]
Documentation: [2]


v3 marks a major re-haul of the SatNOGS Rotator design, with learnings from v2 applied. You can see a lot of the thinking and background research that was conducted prior to v3 development in this thread.

Also in this list is presented different rotators, either commercial or DIY builds.


SatNOGS v3 Rotator
Plastic Parts 26
Non Printed Parts approx. 345
Cost ~ $220
Controller Electronics SatNOGS Rotator Controller
Type AZ/EL (possible X/Y)
Motors 2x NEMA 17 Stepper or 2x DC Motors
Frame Material Aluminum T-slot 20x20
Speed (deg/sec)  ? (Stepper motor), ? (DC motor)
Torque (Nm) ~? (Stepper motor), ~? (DC motor)
Brake Torque (Nm)  ?
Dimensions (mm) 306.5x197x142.5 (AZ/EL)
Weight (kg) 6.2

Brake Torque

The greatest force the tracker needs to withstand is the force created by strong wind. The worst case is when one antenna is elevated at 90 degs, facing the direction of the wind. We based our calculations on an article found online after comparing it to others. We “translated” the second table in metric (because we don’t understand imperial and because we needed same units system in our calculations)

Method Wind Zone(km/h) Height (m) Pressure(N/m^2)
EIA-222-C 160 N/A 1280
EIA-222-F 128 14 1260
EIA-222-F 128 21 1390
EIA-222-F 128 30 1500
UBC'97 128 14 1290
UBC'97 128 21 1160
UBC'97 128 21 1390
UBC'97 128 30 1260
UBC'97 128 42 990
UBC'97 128 42 1360
Generic Formula 150 N/A 1270

and we applied the worst case model (EIA-222-F) in 3 different antennas: in the biggest one of our designs, and in two others, for which we obtained data from yaesu G800 rotator manual at page 3. We assumed that antennas are mounted in 1m away from the azimuth axis. For our antenna with 2m length (actual, not wavelength), made by 2cm square tube, the generated torque was ≈600Kg*cm. For the 144MHz 10-elements Yagi from the article is ≈6000Kg*cm and for the third 430MHz, 12-elements Yagi is ≈1800Kg*cm

Moment of inertia

Now for the moment of inertia: (for all installation methods we assumed that antennas are counterbalanced in the elevation axis) the worst case scenario here is to use two 3kg (our designs are less than 1kg) back mounted yagis with 3kg counterbalances both mounted in 0.75m away from azimuth axis. The torque you need in order to accelerate this system from ω=0deg/s angular velocity to ω=5deg/s (the math about angular velocity is below) in one second is about 60kg*cm.

Note: we suppose that the mass of antennas is near to the altitude axis, so the torque of this axis that is needed to accelerate is approximately 0.

  • M1: torque of Azimuth axis
  • L: length of center of mass of antennas from azimuth axis (0.75m)
  • m: mass of antennas and of counterweight (3kg + 3kg = 6kg)
  • I: moment inertia
  • a: angular acceleration of azimuth axis 5deg/s^2
  • I = I1 + I2 = m*L^2 + m*L^2 = 2*m*L^2 = 6.75 kg*m^2
  • M1 = I*a = 6.75kgm^2 * 0.087rad/s^2 = 0.58 Nm = 5.8 kgm = 58 kgcm

Angular velocity

(How well do you remember trigonometry?)For the angular velocity max needed in altitude axis the things are straightforward. The closer is the satellite the larger the velocity. According to the wikipedia article about LEO, the lowest height limit is 160 km and the speed unit to orbit earth in this altitude is 7,8 km/s. As a result, maximum velocity in ALT axis is 2,8 deg/s. In ALT AZ rotator design there is a well known limitation: the closer something passes near zenith the biggest gets the velocity of the AZ axis. Therefore, we have analyzed this problem to figure out the optimal velocity and how high we are allowed to track a target in relation to AZ velocity. The picture below illustrates a ground station B which tracks a satellite Γ in X degrees altitude. The satellite velocity at this point is vertical to the screen (page) plane.

Angular Velocity

The equations that lead to maximum altitude at which we can track in relation to AZ angular velocity are

  • ω : angular velocity of AZ DOF in rad/s
  • H = ΑΕ + ΕΓ : Minimum Height of LEO, 160 km
  • R = ΑΕ : Radius of Earth, 6500 km
  • u : linear velocity of satellite that rotates in 160km height is 7.8 km/s
  • ΒΔ = u / ω : ΒΔ in km
  • α = atan(ΒΔ / R)
  • δ = π - α
  • γ = asin( sqrt(R^2+ΒΔ^2) * sin(δ) / (H+R) )
  • ά = π - δ - γ
  • ΓΔ = (H+R) * sin(ά) / sin(δ)
  • χ = atan(ΓΔ / ΒΔ)

Below you can see the plot of the equations mentioned above, where horizontal axis represents angular velocity (ω) in deg/s and vertical axis shows the max track altitude (χ) for lower bound of LEO.

Angular Velocity Plot

After studying this diagram, we came up to the conclusion that an angular velocity of 5 deg/s is adequate. For this decision, we took into consideration the main lobe of antenna (Δ3db) which in most situations is about 20 deg.

General Specifications

Together with the above mentioned specifications, we would also like for the 3rd version of SatNOGS rotator to be:

  • inexpensive (less than €300, if possible)
  • lightweight and portable (~6Kg, size:~300x~150x~150mm)
  • rigid and durable
  • easy to build and fix (try to use easily available materials)
  • weatherproof
  • electromagnetically shielded, so that noise in reception is reduced
  • accurate (<1deg, backslash reduction and use of encoders at the axis)


3d Printing at a Fab Lab or your local hackerspace: If you don't have your own 3d printer, then a local Fab Lab or hackerspace may be able to do it for you. Fab Labs and hackerspaces are places that have invested in the machinery and you can take the designs to them. Generally they need .stl files to import into the software that runs the machines, but this should be discussed with the Fab Lab or hackerspace. You then pay for the material, time or a combination of the two for each of the parts or any other agreement in place.

Most people building the rotator have had success builds with simple ABS material for the 3D printing parts.

T Slot - If you don't want to cut the pieces yourself, then you may be able to find a supplier that will do this for you. (Here's one in the United Kingdom.)

Hidden corner connectors - AliExpress gave the cheapest supplier

A good US source is MISUMI-USA; they will also cut to length. MISUMI has several other global locations [3].

Beware, the 20-series T-slot from 80/20 Inc. in the US has slots that are only 5.2mm wide. The hidden corner connectors from e.g. AliExpress will not fit.

Stepper Motors - eBay

Belts - eBay

Fixings / Pipe - eBay

Part Fabrication

Most of the parts could be fabricated by a FDM 3D-printer. Some parts have only 2D geometry so could be fabricated by a laser cutter. Other parts have modifications of common(hardware) parts like threaded rods or aluminum pipes.

Build Sequence

Mechanical Analysis [WIP]

Horizontal distance between pulleys (P1, P2) is 58mm. Vertical distance between pulleys (P1, P2) is w = 9.5mm.

Pulleys and Belt are GT2, 2mm pitch. Belt width, 6mm. Belt thickness, 1.38mm (0.76 tooth).

Wrap angle in both pulleys is larger than 60deg. At least 6 teeth in contact with the pulley at any given time. In practice that means you want a minimum of a 12 tooth pulley, and usually try to get at least 18 teeth.

Outer Diameter of pulleys:

P(T) | OD(mm)
16 | 10.2
20 | 12.7
36 | 22.9
40 | 25.5

Belt calculation (according to calculator):

Ratio | P1(T) | P2(T) | Belt(T) | L(mm)

Motor Maximun no-load speed, 200RPM = 1200deg/s Motor Maximum stall-torue, 1.2Nm

Angular Velocity

Position of idler do not care, or min 1.3*P1, max 1.5*P1 (for 20T, ~16mm/~20mm).

Belt gear selection:

  • 20/36 with 1.8 ratio and 86T/172mm belt without idler
  • 20/40 with 2 ratio and 90T/190mm belt with idler

To calculate Deflection force, (page T-31, sdp - design-guidelines)

/ \
P1 P2
  • Determination of design load

According to perfomance graph of DC motor, the optimal output power is Tm = 0.6Nm with efficiency of 0.2 and 100RPM = 600deg/s. Select a service factor of 1.5 (service factors between 1.5 and 2.0 are generally recommended when designing small pitch synchronous drives). Tpeak = SF*Tm = 1.5*0.6 = 0.9Nm

  • Choice of belt pitch

Due to backslash and accuracy in both directions of movements and volume constrains, we choose GT2, pitch 2mm.

  • Check belt pitch selection based on individual graphs

Due to Tpeak = 0.9Nm No-load speed,(Speed of fastest shaft) = 100RPM = 600deg/s GT2 pitch 2mm belt is the better solution for our application.

  • Determine speed ratio

Speed ratio 1.8-2.25 according to specification of output rotation speed of 5deg/s.

  • Check belt speed

V(m/s) = 0.0000524 x pulley PD (mm) x pulley rpm = 0.066548m/s Belt speeds up to 6,500 fpm (33.02 m/s) do not require special pulleys.

  • Determine belt length

Table 'Belt calculation (according to calculator)' Teeth in mesh: 9

  • Determine the belt width

From Table 43 torque = 0.17Nm Length Correction Factor = 0.9 width multiplier = 1.00 torque*Length Correction Factor*width multiplier = 0.17*0.9*1.00 = 0.153Nm Teeth in mesh: 9 Tpeak = 0.9Nm, so belt width is nice for our application

  • Check the number of teeth in mesh

Teeth in mesh: 9 according to calculator

  • Determine proper belt installation tension

SECTION 10, on page T50, look at 'To calculate Deflection force, (page T-31, sdp - design-guidelines)'

  • Y = 2.05, Tst = 0.812*DQ/d + mS^2 = 12.8lb + 0 = 5.8kg
  • DQ = Tpeak = 0.9Nm = 7.9lb-in
  • d = 12.7mm = 0.5in
  • S = (0.5*100/3.82)/1000 = 0.0131ft/min
  • m = 0.039
  • span length, t = sqrt(CD^2 - (PD-pd/2)^2) = 57.64mm
  • Belt pitch length, L = 180mm
  • t/L = 0.32
  • Fd,min = 0.8lb = 0.36kg
  • Fd,max = 0.9lb = 0.41kg
  • Safety factor 1.5
  • P2 timing pulley torque - Maximum radial load of timing belt ball bearing 625zz

Tpeak = 0.9Nm TorqueP2 = 2*0.9Nm = 1.8Nm, PDp2 = 25.5mm Radial static load of 625ZZ is 0.38kN T-39

  • Maximum thrust load of timing belt ball bearing 625zz
  • Maximum radial and thrust load of output ball bearings 6008zz

Calculate or evaluate correct loads for deep groove ball bearings radial static load = 11.6kN thrust static load = 0.7*11.6kN = 8.12kN This type of construction permits the bearings to support relatively high thrust load in either direction. In fact the thrust load capacity is about 70% of the radial load capacity. A ball bearing primarily designed to support radial load can also support high thrust load; because only few balls carry the radial load, whereas all the balls can withstand the thrust load.

  • Maximum self-locking or back-drivable torque of gear box (according to more weak component)

It necessary to achieve [specs](, 60Nm (6Kg in 1 meter)

  • Nominal torque of drivable torque of gear box (according to more weak component) and maximum rotational speed of gear box


Worm Gear Box Calculations

  • Gear ratio: i12 = 30
  • Angle between axis of gears: δ = 90 deg
  • Number of threads in worm: If i12 >= 30 then z1 = 1
  • Number of teeth in worm wheel: z2 = i12*z1 = 30
  • Center distance: initial case a = 45.5 mm
  • Worm reference diameter: AGMA d01>= 11.5*(a/25.4)^0.875 = 19.15 mm, so d01 = 19.5mm
  • Worm wheel reference: d02 = 2*a - d01 = 71.5 mm
  • Axial module: ms = d02/z2 = 2.38 , so ms = 2.5

Recalculate d02, a with new axial module

  • d02 = z2*ms = 75mm, a = (d02+d01)/2 = 47.25mm
  • Axial pitch: ts = π*ms = 7.854mm
  • Reference lead angle: γ0 = atan(d02/(i12*d01)) = 7.3 deg
  • Worm tip diameter: dk1 = d01 + 2*hk = 24.5mm
    • Worm teeth reference addendum in axial section: hk = hk* *ms = 2.5mm
    • Worm tooth reference addendum coefficient: hk* = 1
  • Worm root diameter: df1 = d01 - 2*hf = 13.5mm
    • Worm tooth reference dedendum: hf = hf* _ms = 1.2_ms = 3mm
    • Dedendum coefficient: hf* = 1.2
  • Worm length: L = 2.5_ms_sqrt(z2+2) = 35.36mm
  • Worm tooth thickness: smx1 = smx1* * ts = 3.927mm
    • Tooth thickness coefficient: smx1* = 0.5
  • Normal pressure angle: aon = 20 deg
  • Worm wheel throat diameter: dk2 = d02+2*hk = 80mm
  • Worm wheel root diameter: df2 = d02 - 2*hf = 69mm
  • Worm wheel outside diameter: de2 = dk2 + 2*mx = 83.5mm
    • Worm wheel tooth external addendum: mx = n*ms, 0.4<=n<=1.5
  • Effective worm wheel face width: b2H,max = sqrt((2_a - df2)^2 - (2_a - de2)^2) = 23mm

Test Sequence

Test sequence needed