Dusterloh 15471160 A 3/3 Way Valve

Hydraulic gear motors Hydraulic brake gear motors
Catalogue Edition Page
Design notes
GM1 - 010 EN 2023.01 / 06 9
Design Hydraulic gear motors are designed based on a number of criteria:
• • • • •
Maximum or continuous transmission output performance Maximum or continuous transmission output torque
Maximum required output speed Radial or axial load transmission on transmission output shaft
Required holding torque when using a multi-disc brake
Normally, the design process follows these steps:
Definition and/or calculation of the loads to be raised on the transmission output shaft
• • • • • •
Maximum transmission torque as a short-term peak value at, e.g., 5% ED/h
Nominal torque to be transmitted continuously by the gear, i.e., at 100% ED
Speed range, i.e., minimum and maximum speed of the transmission output shaft
The performance data required based on these values Any potential radial and axial loads
The differential pressure available in the hydraulics for reaching the torques
Based on the existing and/or calculated power data, such as nominal or continuous performance and maximum performance
at, e.g., 5% ED/h, you pre-select the required motor size (e.g., as per overview HM1-002 or catalogues HM1-014 and/or HM1015). Following this, use the corresponding tables for making your selection. Here, the individual data, which generally refer
to the transmission output shaft, have the following meaning:
i Vg T spez T dauer T max kd km n min - n max Pd
Effective transmission ratio of the gear Geometric displacement in cm³/U
Mean specific torque in Mn/bar Admissible continuous torque in Nm at delta p d in bar
Maximum admissible operating torque in Nm at delta p m in bar and 5% ED/h
Service factor for the continuous capacity of the gears relating to T continuous
Service factor for the continuous capacity of the gears relating to T max
Operating speed range in min -1 Maximum admissible output continuous performance. In case values are continuously exceeded
you need to provide for a gearing purge and/or a gear oil cooling.
The dimension tables also specify admissible radial and axial loads, regarded as a singular force, for each gear size. The
calculations are based on a working life of
F ad/s
F r3
F r2
F r1
F r3
Admissible radial force for linear measure E = E Admissible radial force for linear measure E = E/2
Admissible radial force for linear measure E = 0 Admissible axial force, dynamic
Admissible axial force, static Output speed Nominal bearing working life
F r2
F r1 F r2 F r3 F ad F as n2 L h10
F r1
n 2 * L h10 = 10 5
F ad/s E
E
Apart from the actual design data such as torque, speed etc., factors such as the operating medium used, operating and
ambient temperatures, operating mode, installation position, potential radial and axial forces or requested bearing working
life, even gear-changing and/or starting up frequency in case of holding brakes, play a role. This is why no calculation formulas are listed here. We therefore recommend not to use your own calculations but to make use of our complimentary design
service. Please contact our back office staff and/or our technical field offices or simply fax us the request form (with as much
information entered as possible) and we will send you our suggestion for a solution and a detailed offer as soon as possible.
Q DÜSTERLOH Fluidtechnik GmbH * Im Vogelsang 105 * D - 45527 Hattingen * +49 / (0) 2324 / 709-0 *
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