RU2176939C2 - Hydrostatodynamic liquid-friction bearing assembly for rolls of rolling mills - Google Patents

Abstract

FIELD: rolled stock production, namely bearing assemblies of rolls of sheet rolling mills. SUBSTANCE: hydrostatodynamic bearing assembly includes housing, insert-sleeve with hydrostatic pockets and ducts connecting (through throttles) pockets with high-pressure lubrication system. Position of geometry centers of hydrostatic pockets is determined according to relation li/Ln= 0.83-0.94, where i - sequence number of pockets beginning from end of insert-sleeve at side of roll barrel until mean point of length of insert-sleeve; n - sequence number of pocket beginning from end of insert-sleeve at side opposite to roll barrel until mean point of length of insert-sleeve at even number of pockets and until mean pocket (including the last) at odd number of pockets; lidistance from end of insert-sleeve at side of roll barrel until geometry center of single or each pocket arranged between said end and mean point of length of insert-sleeve; Ln- distance from end of insert-sleeve at side opposite to roll barrel until geometry center of each of pockets arranged between said end and mean point of length of insert-sleeve at even number of pockets and until single or mean pocket (including the last) at odd number of pockets. EFFECT: increased loading capacity of bearing assembly, its high repairability, simplified mounting, enhanced process of manufacture. 3 dwg _

Description

 The invention relates to the field of rolling production, and more specifically to the supports of the rolls of sheet rolling mills.

 Currently used as bearings of rolling rolls, hydrostatic dynamic fluid friction bearings have limitations in load capacity and rotation speed, which are largely affected by the pressure of the supplied hydrostatic lubricant, which in turn is limited by the capabilities of the hydraulic equipment used.

 Known hydrostatodynamic bearing for rolls of rolling mills (see ed. Certificate of the USSR N 329915, class B 21 B 31/00, decl. 02.12.70, publ. 24.02.72), including a housing, a liner, a cavity high pressure of the working fluid, made in the housing or in the liner, and channels along the length of the bearing, multi-row placed along the arc of the working area, connecting the high-pressure cavity with the working surface of the liner.

 The multi-row arrangement of the channels along the arc of the working zone of the bearing helps to equalize pressure and temperature in diametric sections. However, in the axial section of the bearing during misalignment of the roll journal relative to the liner in the larger clearance zone, the high-pressure lubricant consumption increases, although this is not necessary, since the temperature in the larger clearance zone is less than in the smaller one. While maintaining the performance of the hydrostatic lubrication system, the pressure in the working fluid cavity decreases, the bearing capacity of the bearing decreases, and the lubricant consumption is used inefficiently.

 Of the known closest in technical essence (prototype) is a hydrostatodynamic fluid friction bearing for rolls of rolling mills, described in the USSR author's certificate N 810315, class. B 21 B 31/02, claimed 02/12/79, publ. March 7, 81

 This hydrostatodynamic bearing includes a housing, an insert sleeve with hydrostatic pockets on its working surface and channels connecting pockets through the chokes to a high-pressure cavity made in the housing and connected to a high-pressure lubrication system. Chokes are made with different hydraulic resistance. At the same time, in the channels connecting the hydrostatic pockets to the high-pressure cavity located closer to the roll barrel, throttles with the least hydraulic resistance are installed, and in the channels connecting the hydrostatic pockets to the high-pressure cavity located closer to the end of the insert sleeve opposite the roll barrel, chokes with the highest hydraulic resistance are installed. Thus, through the throttle with the smallest hydraulic resistance, the lubricant enters the more loaded gap area between the roll pin and the liner located on the side of the roll barrel (the size of this gap, as measurements show, is usually less than from the side opposite to the roll barrel ) This allows you to increase the pumping of lubricant through the loaded region of the gap and thereby reduce the maximum temperature, increase the pressure in the pockets of this region due to a smaller pressure drop on the throttle and increase the bearing capacity of the lubricating layer of this region. As a result, the temperature is equalized along the length of the bearing.

 A disadvantage of the known hydrostatodynamic bearing is the need to use chokes with different hydraulic resistance, as this complicates the design, reduces its maintainability, complicates installation. Since the throttles used for various hydrostatic pockets of the liner bushings are not interchangeable, the installation requires increased attention and qualification of the operating personnel. In the case of improper installation of the chokes, the load capacity and durability of the hydrostatodynamic bearing are sharply reduced.

 The objective of the present invention is to provide a hydrostatodynamic bearing with high load capacity, while having high maintainability, manufacturability, simplicity and ease of installation.

где i - порядковый номер кармана, считая от торца втулки-вкладыша со стороны бочки валка до середины длины втулки-вкладыша; n - порядковый номер кармана, считая от торца втулки-вкладыша со стороны, противоположной бочке валка, до середины длины втулки-вкладыша при четном числе карманов и до среднего кармана включительно, если число их нечетное; l_i - расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра единственного или каждого из карманов, расположенных между упомянутым торцом и серединой длины втулки-вкладыша; L_n - расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка, до геометрического центра каждого из карманов, расположенных между упомянутым торцом и серединой длины втулки-вкладыша при четном числе карманов и до единственного или среднего кармана включительно, если число их нечетное.The problem is achieved in that in a hydrostatodynamic fluid friction bearing for rolls of rolling mills, comprising a housing and a liner with hydrostatic pockets on its working surface and channels connecting these pockets through the chokes with a high pressure lubrication system, according to the invention, the position of the geometric centers of the hydrostatic pockets determined from the ratio

where i is the serial number of the pocket, counting from the end of the liner from the side of the roll barrel to the middle of the length of the liner; n is the ordinal number of the pocket, counting from the end of the liner from the side opposite to the roll barrel, to the middle of the length of the liner with an even number of pockets and to the middle pocket inclusive if their number is odd; l _i is the distance from the end of the insert sleeve from the side of the roll barrel to the geometric center of the only or each of the pockets located between the end face and the middle of the length of the insert sleeve; L _n is the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of each of the pockets located between the said end and the middle of the length of the insert sleeve with an even number of pockets and to a single or middle pocket, inclusive, if their number is odd.

 This design provides a more rational arrangement of hydrostatic pockets along the length of the liner, in which all the pockets are shifted towards the roll barrel relative to the middle of the length of the liner, due to which the hydrostatic force created in them allows to increase the bearing capacity of the hydrostatic lubricant layer, since it is most efficient balances the external load on the working surface of the liner, the total application line of which, as shown by experiments, as a rule о, is shifted towards the roll barrel relative to the axis of the stand press screws due to the bending of the rolls under the action of the pressure force of the rolled metal on the rolls.

При отношении

смещение результирующей гидростатической силы в сторону бочки валка будет слишком велико, что приведет к перекосу втулки-цапфы относительно втулки-вкладыша при снижении внешней нагрузки, например, при прокатке более пластичных металлов и повреждению антифрикционного слоя втулки-вкладыша. При

смещение результирующей гидростатической силы в сторону бочки валка очень мало и не приводит к увеличению грузоподъемности подшипника.This allows you to simultaneously provide high load capacity without increasing pressure in the high pressure lubrication system, as well as high maintainability, manufacturability and ease of installation of the bearing due to the possibility of using chokes with the same hydraulic resistance for pockets. The most optimal, as experiments show, is the ratio

With respect

the displacement of the resulting hydrostatic force towards the roll barrel will be too large, which will lead to a misalignment of the journal sleeve relative to the insert sleeve while reducing the external load, for example, when rolling more ductile metals and damage to the antifriction layer of the insert sleeve. At

the displacement of the resulting hydrostatic force towards the roll barrel is very small and does not lead to an increase in bearing capacity.

To explain the invention, a specific embodiment of the invention is given below with reference to the accompanying drawings, in which
in FIG. 1 shows a hydrostatodynamic fluid friction bearing for rolls of rolling mills, axial section;
in FIG. 2 - liner with an even number of hydrostatic pockets in axial section with a distribution diagram of the load acting on it;
in FIG. 3 - liner with an odd number of hydrostatic pockets in axial section with a distribution diagram of the load acting on it.

в котором i - это порядковый номер кармана, считая от торца втулки-вкладыша 2 со стороны бочки валка 10 до середины длины 0-0 втулки-вкладыша 2; n - это порядковый номер кармана, считая от торца втулки-вкладыша 2 со стороны, противоположной бочке валка 10, до середины длины 0-0 втулки-вкладыша 2 при четном числе карманов и до среднего кармана включительно, если число их нечетное; l_i - это расстояние от торца втулки-вкладыша 2 со стороны бочки валка 10 до геометрического центра единственного или каждого из карманов, расположенных между упомянутым торцом и серединой длины 0-0 втулки-вкладыша 2; L_n - это расстояние от торца втулки-вкладыша 2 со стороны, противоположной бочке валка 10, до геометрического центра каждого из карманов, расположенных между упомянутым торцом и серединой длины 0-0 втулки-вкладыша 2 при четном числе карманов и до единственного или среднего кармана включительно, если число их нечетное. Например, когда карман во втулке-вкладыше единственный, i = N 1, n = N 1, l₁ - расстояние от геометрического центра кармана до торца втулки-вкладыша со стороны бочки валка, L₁ - расстояние от геометрического центра кармана до торца втулки-вкладыша со стороны, противоположной бочке валка. Отношение расстояния l₁ к расстоянию L₁ выполняют равным

При нечетном числе карманов во втулке-вкладыше, равном, например, 5 (см. фиг. 3), порядковые номера i карманов, расположенных между торцом втулки-вкладыша со стороны бочки валка до середины длины 0-0 втулки-вкладыша, будут: N 1, N 2, N 3. Порядковые номера n карманов, расположенных от торца втулки-вкладыша со стороны, противоположной бочке валка, до среднего кармана включительно будут: N 1, N 2, N 3. l₁ в этом случае - расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра первого от этого торца кармана; l₂ - расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра второго от этого торца кармана; l₃ - расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра третьего от этого торца кармана (среднего по отношению ко всем пяти карманам). L₁ - расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка, до геометрического центра первого от этого торца кармана; L₂ - расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка, до геометрического центра второго от этого торца кармана; L₃ - расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка до геометрического центра третьего от этого торца кармана (среднего по отношению ко всем пяти карманам). Отношение расстояний

выполняют равным

При четном числе карманов, например, при наличии во втулке-вкладыше четырех карманов (см. фиг. 2) порядковые номера i карманов, расположенных между торцом втулки-вкладыша со стороны бочки валка и серединой длины 0-0 втулки-вкладыша будут N 1 и N 2. Порядковые номера n карманов, расположенных между торцом втулки-вкладыша со стороны, противоположной бочке валка и серединой длины 0-0 втулки-вкладыша будут: n 1 и N 2. l₁ - расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра первого от этого торца кармана; l₂ - расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра второго от этого торца кармана; L₁- расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка до геометрического центра первого от этого торца кармана; L₂ - расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка, до геометрического центра второго от этого торца кармана. Отношения соответствующих расстояний

выполняют равными

Конкретный пример. Для гидростатодинамического подшипника диаметром 1120 мм и длиной втулки вкладыша 840 мм с двумя гидростатическими карманами по длине подшипника расстояние от торца втулки-вкладыша со стороны бочки валка до геометрического центра кармана, расположенного между упомянутым торцом и серединой длины втулки-вкладыша l₁ выбрано равным 190 мм. При этом расстояние от торца втулки-вкладыша со стороны, противоположной бочке валка до геометрического центра кармана, расположенного между упомянутым торцом и серединой длины втулки-вкладыша L₁ выбирают равным 210 мм, с учетом соотношения

Конкретное соотношение

т.е. входит в оптимальное.The hydrostatodynamic fluid friction bearing for rolls of rolling mills comprises a housing 1, an insert sleeve 2 with hydrostatic pockets 3 on its working surface and channels 4 connecting pockets 3 through a chokes 5 with a channel 6 made in the housing 1 and connected to a high pressure lubrication system 7 , front 8 and back 9 covers. The position of the geometric centers of hydrostatic pockets 3 is determined from the ratio

in which i is the ordinal number of the pocket, counting from the end of the insert sleeve 2 from the side of the roll barrel 10 to the middle of the length 0-0 of the insert sleeve 2; n is the serial number of the pocket, counting from the end of the liner 2 from the side opposite to the roll barrel 10, to the middle of the length 0-0 of the liner 2 with an even number of pockets and to the middle pocket, inclusive, if their number is odd; l _i is the distance from the end of the insert sleeve 2 from the side of the roll barrel 10 to the geometric center of the sole or each of the pockets located between the end and the middle length 0-0 of the insert sleeve 2; L _n is the distance from the end of the insert sleeve 2 from the side opposite to the roll barrel 10 to the geometric center of each of the pockets located between the end and the middle length 0-0 of the insert sleeve 2 with an even number of pockets and to a single or middle pocket inclusive, if their number is odd. For example, when the pocket in the insert sleeve is unique, i = N 1, n = N 1, l ₁ is the distance from the geometric center of the pocket to the end of the insert sleeve from the side of the roll barrel, L ₁ is the distance from the geometric center of the pocket to the end of the sleeve liner from the side opposite to the roll barrel. The ratio of the distance l ₁ to the distance L ₁ is equal to

With an odd number of pockets in the insert sleeve equal to, for example, 5 (see Fig. 3), serial numbers of i pockets located between the end of the insert sleeve from the roll barrel side to the middle of the length 0-0 of the insert sleeve will be: N 1, N 2, N 3. The serial numbers of n pockets located from the end of the liner from the side opposite the roll barrel to the middle pocket inclusive will be: N 1, N 2, N 3. l ₁ in this case, the distance from the end bushings from the side of the roll barrel to the geometric center of the first from this end of the pocket; l ₂ is the distance from the end of the liner from the side of the roll barrel to the geometric center of the second from this end of the pocket; l ₃ is the distance from the end of the insert sleeve from the side of the roll barrel to the geometric center of the third from this end of the pocket (average with respect to all five pockets). L ₁ is the distance from the end of the liner from the side opposite the roll barrel to the geometric center of the first pocket from this end; L ₂ is the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of the second from this end of the pocket; L ₃ is the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of the third from this end of the pocket (average with respect to all five pockets). Distance ratio

perform equal

With an even number of pockets, for example, if there are four pockets in the insert sleeve (see Fig. 2), the serial numbers of i pockets located between the end of the insert sleeve on the roll barrel side and the middle of the length 0-0 of the insert sleeve will be N 1 and N 2. The serial numbers of n pockets located between the end of the insert sleeve from the side opposite to the roll barrel and the middle of the length 0-0 of the insert sleeve will be: n 1 and N 2. l ₁ - distance from the end of the insert sleeve from the side of the roll barrel to the geometric center of the first pocket from this end; l ₂ is the distance from the end of the liner from the side of the roll barrel to the geometric center of the second from this end of the pocket; L ₁ is the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of the first pocket from this end; L ₂ is the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of the second from this end of the pocket. Relations of corresponding distances

perform equal

Specific example. For a hydrostatodynamic bearing with a diameter of 1120 mm and a liner sleeve length of 840 mm with two hydrostatic pockets along the bearing length, the distance from the end face of the liner sleeve from the roll barrel to the geometric center of the pocket located between the said end face and the middle of the liner sleeve length l _{1 is} chosen equal to 190 mm . In this case, the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of the pocket located between the end face and the middle of the length of the insert sleeve L _{1 is} chosen equal to 210 mm, taking into account the ratio

Specific ratio

those. included in the optimal.

 Hydrostatic dynamic fluid friction bearing operates as follows.

величина и положение суммарной гидростатической силы наиболее оптимальны и процесс уравновешивания внешней нагрузки P происходит наиболее эффективно.In the process, lubrication from the high-pressure system 7 through the channel 6, chokes 5 and channels 4 is fed into the hydrostatic pockets 3, creating a hydrostatic force to balance the external load P. Since the axial location of the hydrostatic pockets 3 on the working surface of the liner 2 is made according to the ratio

the magnitude and position of the total hydrostatic force are most optimal and the process of balancing the external load P is most effective.

 The proposed hydrostatodynamic liquid friction bearing for rolls of rolling mills in comparison with the known ones allows, at high load capacity, to increase its maintainability, simplify and unify installation operations.

Claims (1)

A hydrostatodynamic fluid friction bearing for rolls of rolling mills, comprising a housing and an insert sleeve with hydrostatic pockets on its working surface and channels connecting these pockets through the chokes to a high pressure lubrication system, characterized in that the position of the geometric centers of the hydrostatic pockets is determined from the ratio

where i is the serial number of the pocket, counting from the end of the liner from the side of the roll barrel to the middle of the length of the liner;
n is the ordinal number of the pocket, counting from the end of the liner from the side opposite to the roll barrel, to the middle of the length of the liner with an even number of pockets and to the middle pocket inclusive if their number is odd;
l _i is the distance from the end of the insert sleeve from the side of the roll barrel to the geometric center of the only or each of the pockets located between the end face and the middle of the length of the insert sleeve;
L _n is the distance from the end of the insert sleeve from the side opposite to the roll barrel to the geometric center of each of the pockets located between the said end and the middle of the length of the insert sleeve with an even number of pockets and to a single or middle pocket, inclusive, if their number is odd.

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