Abstract:
A decanter centrifuge comprises a drum (1) with a conveyor (2) containing an inlet (4). The liquid to be separated flows in a jet centrally into the inlet (4) towards an end wall (11), at which the liquid is radially distributed and flows axially onwards towards the second end wall (13) through an area of the inlet (4) free of members imparting an angular velocity to the liquid. The inlet (4) is provided with inlet apertures (6) positioned on a radius larger than the radius to the overflow edge (9) at the liquid discharge. The design of the inlet (4) implies that the free liquid surface in the inlet during operation is drawn far towards the axis of the drum, thereby causing excess energy supplied to the liquid during acceleration to the angular velocity of the conveyor (2) to be dissipated in the comparatively thick liquid layer before the liquid discharges into the separation space (7) through the inlet apertures (6).
Abstract:
The decanter centrifuge comprises a drum (1) rotatably journalled in a frame by means of bearings at its ends. The separating compartment of the drum is closed at both ends by means of end walls (4, 5). The drum accommodates a rotatably journalled conveyor (6) with a conveyor body (7) and a screw flight (8). A bearing (10) is located in the end wall (4) at the narrow end of the conveyor (6) and a bearing (11) located at the free end of a trunnion (12) projecting from the end gable (5) into the conveyor body (7) is disposed at the widest end of the conveyor. Due to the short distance between the conveyor bearings (10, 11) the rigidity of the conveyor increases, thereby increasing the first critical RPM of the drum.
Abstract:
The decanter centrifuge (1) comprises a conveyor screw (5) constructed as a hollow body with a lower average density than the lighter liquid phase of the surrounding slurry. The conveyor (5) thus flows in said liquid phase which is utilized in that the one traditional radial bearing of the conveyor is replaced by a radial support bearing (22) which only during starting and stopping of the centrifuge cooperates with the conveyor (5) in order to prevent it from contacting the bowl (2). In operation, the conveyor is thus only supported in the radial direction at the one end, entailing that the flexural rigidity of the conveyor becomes less important to the maximum allowable number of revolutions of the centrifuge which may then be increased for a given centrifuge, thereby obtaining an improved separating effect.
Abstract:
The decanter centrifuge (1) comprises a bowl (2) and a conveyor screw (7) rotatably journalled in the bowl (2) and a reduction gear (22) providing a relative rotation of the screw relative to the bowl. The gear (22) is journalled separately relative to the bowl in separate bearings (25, 26). The housing and the driven shaft of the gear (22) are by means of flexural but torsionally stiff couplings (28, 29) connected with the bowl (2) and the conveyor (7), resp. Said flexural couplings result in that the gear (22) is dynamically insulated from the bowl (2) and does not influence the critical number of revolutions thereof. As a result of this the number of revolutions of the bowl - and thus the maximum allowable number of revolutions of the entire centrifuge - may be increased, thereby offering substantially improved separating properties of the centrifuge as a whole.
Abstract:
The centrifuge has an electric motor (18) of the squirrel cage type for the rotation of the centrifuge drum (2) during centrifugation and an electric control (20) comprising a frequency converter (21) for the control of the RPM of the electric motor (18). When cleaning the drum (2) a frequency converter (21) is coupled into the normal current supply line (25) to the electric motor (18) by means of two change-over switches (22, 23). The nominal power of the frequency converter corresponds to the power consumption of the electric motor (18) when the centrifuge drum (2) rotates at a speed corresponding to the centrifugal force at the internal side of the drum (2) being 1.2 to 0.8 times the gravitational force.
Abstract:
The transmission comprises a hollow input member (1) and a coaxial output member (2) supported for rotation relative to the input member. A positive displacement pump comprises a cylinder block (12) secured to the input member and a rotor (16) which is journalled on an eccentric pin (17) and which drives the pump pistons (15). A positive displacement motor comprises a stator part (6) secured to the input member and a rotor part (5) secured to the output member. The motor cylinders (8) are supplied with hydraulic liquid from the pump through duct means (35, 37, 39) in a disc-shaped control member (22) journalled on the eccentric pin (17) and rotating together with the pump rotor (16). Return flow from the motor to the pump occurs through a space (28) which within the input member surrounds the control member (22) and which communicates with each pump cylinder (14) during the suction stroke of the associated pump piston (15).