• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:

    公开号:SU942606A3
    申请号:SU792837399
    申请日:1979-11-06
    公开日:1982-07-07
    发明作者:Зигг Ханс
    申请人:Мааг-Цанрэдер Унд Машинен Аг (Фирма)；
    IPC主号:
    专利说明:

    The invention relates to mechanical engineering, in particular to sliding bearings with self-aligning segments for high-loaded high-speed shafts, for example, for shafts of turbine plants and turbo gears.
    A sliding bearing is known comprising at least one bearing segment and at least two guide segments and a circulation circuit for supplying a lubricant having a supply pipe for pressurized cooled lubricant C13.
    In this support, despite the cooling of the lubricant in the cooler, friction losses lead to strong heating of the segments, which significantly reduces the specific load capacity of the support and leads to an increase in size.
    A sliding bearing with self-aligning segments is also known, in which, in the intervals between each
    a pair of segments installed two rows of nozzles having a single pressure supply system cooled by liquid lubricant, while nozzles 5 of the first row are located behind the running edge of one of the segments and directed against the direction of rotation of the shaft, and nozzles of the second row are located in front of the running edge of the next segment. This design allows to improve heat transfer in the support [2].
    The disadvantages of this sliding support include the impossibility of completely removing the film of the heated lubricant from the shaft surface, which causes mixing of the cooled lubricant coming from the spray guns with the remaining heated lubricant film and, therefore, rather good cooling conditions are not ensured.
    The aim of the invention is to increase the bearing capacity of the support and reduce its dimensions by improving cooling conditions.
    This goal is achieved by the fact that in the segment bearing of the slide for a highly loaded high-speed shaft containing self-aligning segments, of which at least 5 are at least one bearing and at least two guides, as well as two rows of nozzles installed in the spaces between each pair of segments, a power supply system under pressure with cooled liquid lubricant, while the first row sprayers are located behind the run-down edge of one of the segments and are directed against the direction of rotation of the shaft, and the second row sprayers ts are located in front of the running edge of the next segment, the nozzles are independent, and the power system has channels with different pressures connected to the corresponding nozzles.
    In addition, each of the nozzles can be equipped with a reflective visor for directing and shielding the flow of lubricant. 25
    The bearing segment is made with a groove for draining the grease located in its central part, while the width of the segment is 1.2-2.2 shaft diameters. thirty
    In FIG. I shows a sliding support with a cut in an axonometric projection; in FIG. 2 - cross section of the support.
    Segment support slide ; live shaft 1, rotating in the direction of the arrow (Fig. 2), the housing 2, having an annular groove 3 on the inside. On the surface of the annular groove 3 are supported by rolling bodies 4. The bearing segment 5 located in the lower part of the housing 2, and also two guiding segments 6 located in the upper part of the housing. Each rolling body 4 is fixed with screws 7 on the flat 8 of the corresponding segment. Between each 45 of the guide segments 6 and the corresponding rolling body 4, gaskets 9 are installed, which make it possible to change the corresponding bearing clearance and the offset 50 of the mid-point of support relative to the axis of rotation A of the shaft 1.
    The rolling bodies 4 have a convex outer surface and are made more than 55 narrower than the annular groove 3, which ensures their free angular movement both relative to the axis parallel to axis A and in the perpendicular direction.
    The end surfaces of the rolling bodies perpendicular to axis A limit the angular displacement of the segments in the direction of axis A, and the freedom of movement of the segments in the direction perpendicular to axis A is limited by the stops' 10 fixed in the housing. The width B of the bearing segment 5, measured along axis A, is 1 2 ~ 2.2 diameter D shaft. Both guide segments have a width of approximately half the width of the carrier segment.
    On one end side of the housing 2, a first supply pipe 12 is mounted using brackets 11, which is powered by a cooled lubricant located outside the housing of the support of the pump / cooling unit.
    Three circular pipes 1J are connected to a circular inlet line 12 with first-row sprayers 14, which are installed between each pair of segments, at some distance from the segments parallel to axis A. The sprayers 14 are arranged so that the lubricant jets 15 coming out of them fall onto the shaft at a small distance behind the run-down edge 16 of the adjacent segment at an angle to the shaft against the direction of rotation. Similarly, on the other end side of the housing 2, a second supply pipe 17 is installed with three pipes 18 running parallel to the axis A with sprayers 19 of the second row, which are arranged so that the lubricant jets 20 emerging from them fall onto the shaft 1 at a small distance in front of the running edge 21 adjacent segment at an angle to the shaft in the direction of rotation. On each pipe 13 with nozzles 14 a reflective visor 22 is installed, located parallel to the axis A and the plane of symmetry of the jets 15 of the lubricant, i.e. also mounted at an angle to the shaft against the direction of rotation.
    Similarly, on the pipes 18 with nozzles mounted visors 23, located at an angle to the shaft in the direction of rotation of the shaft 1.
    With the increased width B of the bearing segment, taking into account the intensity of the lubricant, it is necessary that the non-bearing segment be separated in the middle; a circumferential groove 24 for draining the lubricant.
    The cooling of the proposed sliding bearings is carried out as follows 5 .
    Chilled lubricant is independently supplied under pressure to each of the rows of sprayers.
    Moreover, from the sprayers 19 of the second row, i.e. sprayers located in front of the running edge 21 of each segment, the lubricant jets fall into the gap between the segment and the shaft and form a uniform film of lubricant on the shaft surface.
    Through the sprayers 14 of the first row, i.e. sprayers located behind the run-off edge 16 of each segment, supplied with a lubricant independently of the second row, can supply fresh oil with high pressure, due to which the film of the lubricant heated under the segment of lubricant-25 is read out by the shaft with oil streams emerging from these spray guns, so as a last resort only minor residues
    Heated oil can reach the next one, counting in the direction of rotation of the segment. Thus, through the inlet 19 of the second row sprays chilled fresh oil is prevented from mixing with the danger razo-f 35 Greta oil.
    The peeling effect on the one hand, as well as the formation of a uniform film of the lubricant, is enhanced by the presence of reflective visors 40 22 and 23, which direct the jets of lubricant coming out of the spray guns to the shaft 1 and protect it from the lubricant sprayed in the bearing housing. 45
    The jets of lubricant coming out of the individual spray guns first hit the corresponding visor, they turn into a single flattened formation with clearly defined boundaries, which is already sent to the shaft 1 as a common integrated jet of lubricant, as a result of which the lubricant coming from the spray guns 14 of the first row, produces the action of a knife that exfoliates the heated film of the lubricant from the shaft 1. For the same reason, the lubricant coming from spray Ob 4 lei 19 of the second row it immediately forms on the shaft 1 a film of a lubricant of basically uniform thickness, so that the excess of lubricant compared to the amount of lubricant that is able to accommodate the next bearing clearance can be very insignificant, which is caused by the separate power supply of the rows of nebulizers means.
    The implementation of the carrier segment wider than the guide segments is due to the fact that the carrier segment takes up a large specific load, and the implementation of the guide segments of the same width with the carrier segment is impractical, since the heating of the lubricant increases with increasing width of the guide segments.
    For a given maximum allowable value of the specific load on the support, the diameter of the shaft or supporting neck can be taken 1.2 - 2.2 times less, as a result of which the peripheral speed can be reduced in the same ratio, which will reduce friction losses in the gaps and leads to less heat the rubbing surfaces, withstanding due to this higher specific load.
    This design of the sliding support provides good cooling at a moderate consumption of the lubricant at high permissible specific loads, which ultimately provides the possibility of reducing the diameter of the supporting journal, i.e. reduction of support dimensions.
    权利要求:
    Claims (2)
    [1]
    The invention relates to mechanical engineering, in particular to sliding bearings with self-aligning segments for highly loaded high speed shafts, for example for turbine shafts and turbo gears. A known slide bearing, comprising at least one bearing and at least two guiding segments and a circulation circuit for supplying a lubricant, having a supply pipe for a pressurized cooled lubricant SP. In this support, despite the cooling of the lubricant in the cooler, the friction loss leads to a strong heating of the segments, which significantly reduces the specific load capacity of the support and leads to an increase in size. A slide bearing with self-aligning segments is also known, in which, between each pair of segments, there are two rows of sprayers having a single pressure supply system cooled with liquid lubricant, the first row of sprayers located behind the running edge of one of the segments and directed against the direction of rotation. the second row and the nozzles are located in front of the oncoming edge of the next segment. This design allows for improved heat transfer in support t22. The disadvantages of this sliding support include the impossibility of completely removing the film of heated lubricant from the shaft surface due to which the cooled lubricant coming from the nozzles with the remaining heated lubricant film is mixed and thus does not provide sufficiently good cooling conditions. The aim of the invention is to increase the bearing capacity of the support and reduce its dimensions by improving cooling conditions. This goal is achieved by the fact that in a segment slip bearing for a high-punch high-speed shaft containing self-aligning segments, from which at least one carrier and at least two guides, as well as two rows of nozzles installed between each pair of segments, the power supply system under pressure with cooled liquid lubricant, with the first row of atomizers located behind the running edge of one of the segments and directed against the direction of rotation of the shaft, and the second row of atomizers They are located in front of the leading edge of the next segment, the nozzles are made independent, and the power supply system has channels with different pressures connected to the corresponding pullers. In addition, each of the nozzles can be equipped with a reflective visor for guiding and shielding the lubricant flow. The carrier segment is provided with a groove for discharging lubricant located in its central part, the segment width being 1.2-2.2 of the shaft diameter. FIG. 1 shows a slide bearing with a slit in axonometric projection; in fig. 2 - cross-section of the support. The sliding segment bearing comprises a shaft 1 rotating in the direction of the arrow (Fig. 2), a housing 2 having an annular groove 3 on the inside. On the surface of the annular groove 3, they are supported on the rolling bodies k, located in the lower part of the housing 2 bearing segment 5, and two guiding segments 6 located in the upper part of the housing. Each body 4 rolling fixed with screws 7 on the flatness 8 of the corresponding segment. Between each of the directional segments 6 and the corresponding rolling body A, there are gaskets 9 which make it possible to change the corresponding bearing clearance and the displacement of the center point of the bearing relative to the axis of rotation A of the shaft 1. The rolling bodies have a convex outer surface and are made narrower than the annular groove 3 which ensures their free angular displacement both with respect to an axis parallel to axis A, and in the perpendicular direction. The end surfaces of the rolling bodies perpendicular to axis A limit the limiting angular displacement of the segments in the direction of the axis A, and the freedom of movement of the segments in the direction perpendicular to the axis A is limited to the supports fixed to the body 10. The width B of the supporting segment 5 measured along the axis A em 1,22, 2 diameters .D shaft. Both guide segments have a width B of approximately half the width of the carrier segment. On one end side of the housing 2, the first inlet pipe 12 is installed by means of the clamps 11, which is powered by a cooling lubricant from the pump-refrigeration unit located outside the support housing. Three circular pipes 13 are connected to the circular supply pipe 12 with Il sprays of the first row, which are installed between each pair of segments, at a distance of + 1 from the segments parallel to the axis A. The sprays And are arranged in such a way that the outgoing These streams of lubricant 15 fall onto the shaft at a short distance beyond the running edge 16 of the adjacent segment at an angle to the shaft against the direction of rotation. Similarly, on the other end side of the housing 2, a second feed pipe 17 is installed with three tubes 18 parallel to the A axis with sprayers 19 of the second row, which are arranged so that the lubricant jets 20 coming out of them fall onto the shaft 1 on a small the distance of the adjacent segment 21 in front of the runner at an angle to the hall in the direction of rotation. On each pipe 13 with spray guns I, there is a reflector mounted visor 22 located parallel to the axis A and the plane of symmetry of the lubricant jets 15, i.e. also set at an angle to the shaft against the direction of rotation. Similarly, on tubes 18 with sprays, visors 23 are mounted at an angle to the shaft in the direction of rotation of shaft 1. With an increased width B of the carrier segment, taking into account the intensity of lubrication, it is necessary that the carrier segment be divided among the circumferential groove for draining lubricant. The cooling of the proposed sliding support is carried out as follows. In each of the rows of sprayers, a cooled lubricant is independently supplied under pressure. From the sprayers 19 of the second row, i.e. sprays located in front of the incoming edge 21 of each segment, streams of lubricant enter the gap between the segment and the shaft and form a uniform film of lubricant on the shaft surface. Through the sprayers of the first p sprayers located behind the running edge 16 of each segment, supplied with a lubricant regardless of the second row, fresh oil can be supplied with high pressure, due to which the film of the lubricant heated under the lubricant segment is read off from the shaft by oil springs coming out of THESE sprayers, so that in the extreme case, only minor residues of heated i-oil can barely reach the wind, considering the direction of rotation of the segment. Thus, the freshly cooled butter is supplied through sprays 19 of the second row and the fresh cooled oil is protected from the danger of mixing with the heated oil. The effect of peeling on one side, as well as the formation of a uniform film of lubricant, is enhanced by the presence of reflective peaks 22 and 23, which direct the lubricant jets coming out of the nozzles to the shaft 1 and protect it from the lubricant sprayed in the housing. The lubricant streams coming out of the Separate nebulizers first hit the corresponding visor, they turn into a single flattened formation with clearly defined boundaries, which already as a common combined jet of lubricant is directed onto the shaft 1. As a result, the lubricant entering from the nozzles T of the first row, produces the action of a knife that peels the heated film of the emollient from the shaft 1. For the same reason, the diffuser coming from raspit64 lei 19 of the second p and at the same time it forms on the shaft 1 a film of lubricant of basically uniform thickness, so that an excess of lubricant compared to the amount of lubricant that is able to accommodate the next bearing clearance can be very small, the reason for which is precisely the separate supply rows of sprayers with lubricant. The implementation of the carrier segment is wider than the guide segments, due to the fact that the carrier segment takes a large specific load, and the execution of guide segments of the same width with the carrier segment is not advisable, since the heating of the lubricant increases with increasing width of the guide segments. For a given maximum allowable value of the specific load on the support, the diameter of the shaft or bearing neck can be taken 1.2 - 2.2 times less, as a result of which the circumferential speed can be reduced in the same ratio, which will reduce friction losses in the gaps and leads to less heating of the rubbing surfaces, which withstand a higher specific load due to this. Such a design of the slide bearing provides good cooling with a moderate consumption of lubricant at high allowable specific loads, which ultimately provides the possibility of reducing the diameter of the bearing neck, i.e. size reduction support. Claim 1. Segment slip bearing for high-loaded high-speed shaft containing self-aligning segments, of which at least one carrier and at least two guides, as well as two rows of nozzles installed between each pair of segments, cooled pressure supply system liquid lubricant, with the first row of sprayers located behind the running edge of one of the segments and directed against the direction of rotation of the shaft, and the second row of sprayers are located first The next edge of the next segment, characterized in that, in order to increase the carrying capacity and reduce the size by improving the cooling conditions, the sprays are made independent, and the power supply system has channels with different pressures connected to the appropriate sprays.
    [2]
    2. The support according to claim 1, characterized in that each of the nozzles is provided with a reflective visor for guiding and shielding the flow of lubricant.
    3- The support according to claim 1, characterized in that the carrier segment is provided with a groove disposed in its central part for draining the lubricant, wherein the width of the carrier segment is 1.2-2.2 shaft diameters.
    Sources of information taken into account in the examination
    1. The patent of England No. 1313758, cl. R 16 C 33/02, 1973.
    2. US patent number 4077682,
    cl. Р16 С 17/06, 07.03.78 (prototype).
    16 xTS / J 22
    FIG. 18
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    同族专利:
    公开号 | 公开日
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    引用文献:
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    CH391394A|1961-12-22|1965-04-30|Annen Robert|Fluid friction bearing for radial clearance adjustment|
    FR1446668A|1964-09-10|1966-07-22|Glacier Co Ltd|Thrust bearing|
    CH423370A|1964-10-30|1966-10-31|Sulzer Ag|bearings|
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    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    CH1158678A|CH633867A5|1978-11-10|1978-11-10|TIP SEGMENT RADIAL BEARING FOR HIGH-LOADED, HIGH SPEED SHAFTS.|
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