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![Fig. 1 -The dynamic model of the gearing [4-6].](profile/Wieslaw-Fiebig/publication/309010134/figure/fig2/AS:905133722447877@1592812104907/The-dynamic-model-of-the-gearing-4-6_Q320.jpg)
Vor allem die Druck- und Volumenstrompulsation wird für die Geräuschentwicklung bei Pumpen verantwortlich gemacht. Neueste Untersuchungen aber zeigen, daß dadurch zwar die Geräusch- und Schwingungsentstehung im hydraulischen Leitnngssystem beeinflußt wird, aber die Geräuschabstrahlung der Außenzahnradpumpen selbst hauptsächlich von den Schwingungen...
Contexts in source publication
Context 1
... torque on the gears changes periodically depending on the position of the teeth contact point, which is sealing the delivery area from the suction area. In Fig. 2, two characteristic positions of this point have been shown at which the change of the torque as well as the radial forces on the gears occurs. In the range 0 < ' ðp=zÞ Â ðe À 1Þ the trapped volume is connected with the pressure chamber. In the other phase of the double teeth contact it is connected to the suction chamber; thus, the ...
Context 2
... characteristic positions of this point have been shown at which the change of the torque as well as the radial forces on the gears occurs. In the range 0 < ' ðp=zÞ Â ðe À 1Þ the trapped volume is connected with the pressure chamber. In the other phase of the double teeth contact it is connected to the suction chamber; thus, the contact point S (Fig. 2a) of the preceding tooth pair (at the angle position ' þ ð2p=zÞ) is separating the pressure area from the suction area. The pressure torque on the both gears can be calculated ...
Context 3
... connecting the trapped volume with the suction chamber the contact point P separates the pressure chamber from the suction chamber (Fig. 2b). The torques due to the pressure in the angle range ðp=zÞ Â ðe À 1Þ < ' ð2p=zÞ can be determined ...
Context 4
... Fig. 2, the calculated courses of torques have been shown (t = w/v). From Fig. 2, it follows that the change of the position of the sealing point causes respectively the change in torque on both gears. The frequency of this change is equal to the gearing frequency and can be established ...
Context 5
... Fig. 2, the calculated courses of torques have been shown (t = w/v). From Fig. 2, it follows that the change of the position of the sealing point causes respectively the change in torque on both gears. The frequency of this change is equal to the gearing frequency and can be established from: ...
Citations
... External gear pumps are used in many applications, but their disadvantage is relatively high noise emission. As the causes of hydraulic noise generation are known, in particular, pressure and flow pulsation, trapped oil, pressure build-up and down and cavitation, most of these types of excitation can be largely compensated by various design measures [1,2]. Recent studies show that the pressure and flow pulsations are responsible for the noise and vibration generation in the hydraulic piping system, but not for the noise radiation of the pump itself. ...
... Recent studies show that the pressure and flow pulsations are responsible for the noise and vibration generation in the hydraulic piping system, but not for the noise radiation of the pump itself. The intrinsic noise of the external gear pump is mainly dependent from the vibrations and dynamic loads on the gears [1]. These dynamic loads are transmitted through the bearings on the pump housing and cause vibrations and noise. ...
... Many papers are dealing with the definition of dynamic loads inside the sliding bearings of the gear pumps. The first approach has been published in 1990 [1], in which the excitation forces in the gear pump has been defined and the vibration model of the gearing has been described. The current papers regarding the dynamical behavior of gear pumps describe the flow and pressure distribution inside the gear pumps, excitations of gears due to the pressure and dynamical forces in the bearings are calculated [3]. ...
This paper presents the model for simulation of vibration and dynamic loads in external gear pumps. The calculation has been carried out in Matlab/Simulink program. The vibrations of gears are excited due to the variable pressure forces and variable stiffness of the gearing. In this model the stiffness and damping coefficient of sliding bearings as well as the bending stiffness of gear wheels have been included. The influence of pressure and rotational speed on the dynamic forces in the bearings have been analyzed.
Zugl.: Stuttgart, Universiẗat, Diss., 2000.
