Theoretical determination of the characteristics of pliant and loose gland packings
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In stuffing box seals flaky and loose fibrous materials are used extensively as packings. The properties of these materials can be used to the maximum in stuffing boxes of a modified design for sealing shafts and spindles [i, 2]. As found by investigations, a good sealing effect and reduced frictional losses can be ensured by using these materials for sealing shafts, rods, or plungers during their operation in stuffing box seals with a tightened clamping bush when the stuffing box chamber is conical, which expands with increase of the distance from the surfce of the clamping bush at a constant shaft or rod diameter.The referred type of stuffing boxes can be calculated by using the relationships given in [3] where due attention was paid to the effect on the computation characteristics of the static friction along two surfaces limiting the packing under the assumption that no friction occurs between the packing and one limiting surface (chamber). When this is taken into consideration, the calculating relationships become simple and acquire the following form:for determining the tightening forcefor determining the frictional forcewhere F t and Ff are respectively the tightening and frictional forces; d c and d s, respectively, the diameter of the stuffing box chamber and the shaft; s D and h, respectively, the starting width of the packing and its height (Fig. 1); fk, fs, an~ k, respectively, the coefficients of kinetic friction, static friction of the packing against the shaft, and side pressure; ps leakproofing pressure.Appropriate experiments were performed to check the validity of the above postulate. The investigations were conducted on a setup whose design was described in [4]. In this setup the outer replaceable cylindric hub forming the stuffing box chamber was replaced by a hub with an inner conical surface. The experiments were performed with two packings: loose fibrous composite applicable for making the rings AG-50 and with a pliant packing [5] by a procedure adopted earlier [4, 5] at the clamping bush pressures Pc up to i0 MPa, at the spindle diameter d s = 40 n~n, and at the initial width of the packing material Sp = i0 llml.The stuffing box chamber and the spindle were made of steel 45 and had ground working surfaces (8th class of roughness). In the testing process the packing was compacted and its height varied with the pressure of the clamping bush. At Pc = 3-10 MPa the height of the packing of the loose fibrous composite was 0.071-0.059 m and of the pllantpacking was 0.08-0.078 m. The friction moment was measured by a torque wrench with a smooth turn of the spindle. In this case the rate of spindle sliding was 0.001-0.003 m/sec.The experimental data depicted in Figs. 2 and 3 for checking the scope of application of Eqs. (I) and (2) for calculations under the test conditions. These data permit them to be compared with the calculated values of the pressure p= transmitted to the chamber
In stuffing box seals flaky and loose fibrous materials are used extensively as packings. The properties of these materials can be used to the maximum in stuffing boxes of a modified design for sealing shafts and spindles [i, 2]. As found by investigations, a good sealing effect and reduced frictional losses can be ensured by using these materials for sealing shafts, rods, or plungers during their operation in stuffing box seals with a tightened clamping bush when the stuffing box chamber is conical, which expands with increase of the distance from the surfce of the clamping bush at a constant shaft or rod diameter.The referred type of stuffing boxes can be calculated by using the relationships given in [3] where due attention was paid to the effect on the computation characteristics of the static friction along two surfaces limiting the packing under the assumption that no friction occurs between the packing and one limiting surface (chamber). When this is taken into consideration, the calculating relationships become simple and acquire the following form:for determining the tightening forcefor determining the frictional forcewhere F t and Ff are respectively the tightening and frictional forces; d c and d s, respectively, the diameter of the stuffing box chamber and the shaft; s D and h, respectively, the starting width of the packing and its height (Fig. 1); fk, fs, an~ k, respectively, the coefficients of kinetic friction, static friction of the packing against the shaft, and side pressure; ps leakproofing pressure.Appropriate experiments were performed to check the validity of the above postulate. The investigations were conducted on a setup whose design was described in [4]. In this setup the outer replaceable cylindric hub forming the stuffing box chamber was replaced by a hub with an inner conical surface. The experiments were performed with two packings: loose fibrous composite applicable for making the rings AG-50 and with a pliant packing [5] by a procedure adopted earlier [4, 5] at the clamping bush pressures Pc up to i0 MPa, at the spindle diameter d s = 40 n~n, and at the initial width of the packing material Sp = i0 llml.The stuffing box chamber and the spindle were made of steel 45 and had ground working surfaces (8th class of roughness). In the testing process the packing was compacted and its height varied with the pressure of the clamping bush. At Pc = 3-10 MPa the height of the packing of the loose fibrous composite was 0.071-0.059 m and of the pllantpacking was 0.08-0.078 m. The friction moment was measured by a torque wrench with a smooth turn of the spindle. In this case the rate of spindle sliding was 0.001-0.003 m/sec.The experimental data depicted in Figs. 2 and 3 for checking the scope of application of Eqs. (I) and (2) for calculations under the test conditions. These data permit them to be compared with the calculated values of the pressure p= transmitted to the chamber
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