OBRABOTKAMETALLOV Vol. 23 No. 3 2021 MATERIAL SCIENCE EQUIPMENT. INSTRUMENTS 7 1 5 – the resistance forces torque has been determined, both for each camshaft individually and for the total torque; – the power required for homogenization with the proposed new drive was determined. Research methodology The first step in this research involved determining the technological load during the homogenization process in processed cheese manufacturing. According to [37], the operating pressure in the cylinder cavity at the moment of liquid injection is 20 MPa. With a plunger diameter of d = 28 mm and a production capacity of 550 L/h, and a main shaft rotation speed of n = 180 min−¹, the required force exerted by the plunger on the liquid in the homogenizing head’s passage section was determined to be F = 12,315 N. Kinetostatic analysis of this mechanism indicated that the required power consumption for this case is 3.8 kW. The details of the cam-driven homogenizer design proposed by the authors are presented below. Fig. 1 illustrates the locations of the drive cams and pushers driving the plungers. Functionally, all other elements operate in the same manner as in drives with crank mechanisms. Detailed information about the design of the homogenizer can be found in [37]. Fig. 1. The proposed design of a cam-driven homogenizer Numerous motion laws are applicable to cam mechanisms in mechanics. To select an motion law, we propose considering three common types: – simple harmonic motion law; – double harmonic motion law; – cycloidal motion laws [7, 12, 13–27, 31–35, 38–41]. The design scheme for the cammechanism is shown in Fig. 2. The following parameters were considered as variables: profile angles β; phase angles of motion for ascent and descent – φ1, φ2, φ3, φ4; the maximum displacement of the pusher is Smax; current value of the cam rotation angle φ. Due to the fact that all calculations were performed using a mathematical software package, the following notation was adopted for clarity: displacement s(φ); velocity v1(φ); acceleration a1(φ);and torques on the working shaft M1(φ), M2(φ), M3(φ), corresponding to the three cams involved in the design; coefficients for the harmonic motion law max 1 2 S k = , 3 max 2 3 6 k S = − ϕ ; workload forces during product injection and suction, F1, F2, which were assumed to be F1 = 12,315 N and F2 = 2,500 N, respectively.
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