SU894240A1

SU894240A1 - Precision safety friction coupling

Info

Publication number: SU894240A1
Application number: SU802895882A
Authority: SU
Inventors: Яков Иванович Есипенко; Михаил Петрович Гончар; Геннадий Романович Валиулин
Original assignee: Киевский Технологический Институт Пищевой Промышленности
Priority date: 1980-03-19
Filing date: 1980-03-19
Publication date: 1981-12-30

Description

Изобретение относится к машиностроению и может быть использовано в приводах различных машин и механизмов.The invention relates to mechanical engineering and can be used in drives of various machines and mechanisms.

Известна предохранительная муфта, содержащая ведующую и ведомые полумуфты, соединенные фрикционными дисками, поджатыми нажимным диском с помощью регулируемых пружин, а также отжимные элементы, выполненные в виде бочкообразных роликов, установленных в сепараторе и помещенных в радиальных пазах обоймы, зекреплен, ных на упорном стакане и на нажимном диске [Q.Known safety clutch containing the leading and driven half-couplings connected by friction discs, pressed by a pressure disc using adjustable springs, as well as squeezing elements made in the form of barrel-shaped rollers installed in the separator and placed in radial grooves of the cage, secured on the thrust cup and on the pressure plate [Q.

Недостатком известной муфты является сложность изготовления в связи с необходимостью выполнения рабочих поверхностей роликов и обойм с высокой точностью. Наличие большого количества относительных элементов значительно затрудняет монтаж муфты, j Наиболее близкой к предлагаемой является фрикционная предохранитель2 ная муфТа повышенной точности срабатывания, содержащая ведомую и ведущую фрикционные полумуфты, нажимной диск, регулируемые пружины и отжимные элементы в виде центральной шестерни, сателлитов и установленных на их хвостовиках пар винтов и гаек с правой и левой резьбой [2J.A disadvantage of the known clutch is the difficulty of manufacturing due to the need to perform the working surfaces of the rollers and cages with high accuracy. The presence of a large number of relative elements significantly complicates the installation of the coupling, j The closest to the proposed one is a friction fuse 2 nd clutch of increased accuracy, containing a driven and leading friction half-couplings, a pressure plate, adjustable springs and release elements in the form of a central gear, satellites and shanks installed on them pairs of right and left-hand screws and nuts [2J.

Однако недостатками этой муфты являются сложность конструкции и монтажа, малая надежность в работе, вследствие того, что при сборке узлов имеется большое число сопряженных деталей, трудность при изготовлении винтовых пар с несамотормозящейся многозаходной резьбой с относительно большим шагом правого и левого направления.However, the disadvantages of this coupling are the complexity of design and installation, low reliability, due to the fact that when assembling nodes there are a large number of mating parts, the difficulty in manufacturing screw pairs with non-self-locking multi-thread with a relatively large step of the right and left direction.

Цель изобретения - повышение надежности, упрощение конструкции и удобство монтажа.The purpose of the invention is improving reliability, simplifying the design and ease of installation.

Указанная цель достигается тем, что у фрикционной предохранительной муфты повышенной точности срабатыва89^240 4 ния,содержащей ведомую полумуфту и ведущую полумуфту, закрепленную на ведущем валу, нажимной диск, регулируемые пружины, отжимные элементы, выполненные с торцовыми кулачками 5 с рабочей винтовой поверхностью, один из отжимных элементов закреплен на ведущем валу, а другой отжимной элемент смонтирован на нажимном диске. ίοThis goal is achieved by the fact that a friction safety clutch with increased accuracy of operation 89 ^ 240 4 contains a driven half coupling and a driving coupling mounted on the drive shaft, a pressure plate, adjustable springs, release elements made with end cams 5 with a working screw surface, one of the squeezing elements mounted on the drive shaft, and another squeezing element mounted on the pressure plate. ίο

На’ фиг. 1 изображена муфта, продольный разрез; на фиг. 2 - вид с торца на отжимной элемент, закрепленный на ведущем валу: на фиг. 3 - сечение А-А на фиг. 2; на фиг. k - вид 15 с торца на отжимной элемент, смонтированный на нажимном диске; на фиг,5“· сечение В-В на фиг. А.In ’FIG. 1 shows a coupling, a longitudinal section; in FIG. 2 is an end view of a squeezing element mounted on a drive shaft: in FIG. 3 is a section AA in FIG. 2; in FIG. k is an end view 15 of a squeezing element mounted on a pressure disk; in FIG. 5 “; section BB in FIG. A.

Муфта содержит установленную на ведущем валу 1 фрикционную полумуф- _?0ту 2, закрепленную на шпонке 3, ведомую полумуфту А в виде звездочки, нажимной диск 5, поджатый регулируемой пружиной 6, установленной в нажимном диске 5 и упорной шайбе 7, от- _!5жимные элементы 8 и 9 с торцовыми кулачками. Ведомая полумуфта А, установленная между ведущей полумуфтой .2 и нажимным диском 5, центрируется относительно вала наружным диаметром ₃₀отжимного элемента 8 и внутренним диаметром втулки 10 по ходовой посадке.The coupling contains a friction half coupling- _{? 0} tu 2 mounted on the drive shaft 1, mounted on a key 3, a driven coupling half A in the form of an asterisk, a pressure disk 5, preloaded by an adjustable spring 6 installed in the pressure disk 5 and the thrust washer 7, from- _{! 5} clamping elements 8 and 9 with end cams. The driven coupling half A, installed between the driving coupling half .2 and the pressure plate 5, is centered relative to the shaft by the outer diameter _{30 of the} squeezing element 8 and the inner diameter of the sleeve 10 along the landing path.

Отжимной элемент 9 смонтирован на нажимном диске 5 посредством винтов 11. В ступице нажимного диска 5 установлены пальцы 12, которые входят ³⁵свободно в отверстие упорной шайбы 7· Гайка 13 и шайба 1А расположены на резьбе вала 1. Отжимной элемент 8 имеет рабочую винтовую поверхность 15, а отжимной элемент 9 ~ рабочую ⁴⁰винтовую поверхность 16.The squeezing element 9 is mounted on the pressure disk 5 by means of screws 11. In the hub of the pressure disk 5 are pins 12, which enter ³⁵ freely into the hole of the thrust washer 7 · Nut 13 and washer 1A are located on the thread of shaft 1. The squeezing element 8 has a working screw surface 15 and squeezing element 9 ~ working ⁴⁰ screw surface 16.

Муфта работает следующим образом. Движение от вала 1 к звездочке А передается силами трения, создаваемыми по двум плоскостям трения между ⁴⁵нажимным диском 5 фрикционной полумуфтой 2 и звездочкой 4. Сила трения между дисками в соответствующий момент, передаваемый звездочкой А, регулируется изменением деформации пружин ⁵⁰6 посредством гаек 13· В начальный · период процесса передачи крутящего момента вал. 1 с отжимным элементом 8 может поворачиваться относительно всех деталей муфты на небольшой угол, 55 соответствующий зазору между рабочими поверхностями кулачков. Отжимным элементом 8 передается крутящий мо мент звездочке А и всем деталям муфты посредством отжимных элементов 8 и 9.The coupling operates as follows. The movement from the shaft 1 to the sprocket A is transmitted by the friction forces generated by the two friction planes between the ⁴⁵ pressure plate 5 of the friction coupling 2 and the sprocket 4. The friction force between the disks at the corresponding moment transmitted by the sprocket A is controlled by changing the deformation of the springs ⁵⁰ 6 by means of nuts 13 · In the initial period of the torque transmission process, the shaft. 1 with the squeezing element 8 can be rotated relative to all parts of the coupling by a small angle 55 corresponding to the gap between the working surfaces of the cams. With the squeeze element 8, torque is transmitted to the sprocket A and all parts of the coupling by means of squeeze elements 8 and 9.

Угол наклона рабочих поверхностей значительно больше угла трения.The angle of inclination of the working surfaces is much larger than the angle of friction.

При сборке и настройке муфты пружины 6 затягиваются так, что их усилие больше необходимого для передачи заданного момента. Избыточное усилие пружин уравновешивается осевой составляющей усилия, создаваемого кулачками.When assembling and adjusting the clutch, the springs 6 are tightened so that their force is greater than the required torque to transmit. Excessive force of the springs is balanced by the axial component of the force generated by the cams.

Момент передаваемый муфтой определяется по формуле:The moment transmitted by the clutch is determined by the formula:

_{м =} 2Тп __________ ^МП Г 1 2 Ί ’ (1) _{m =} 2Tp __________ ^M P D 1 2 Ί '(1)

L Ref d_ctg(«(.i-p) J где Μ - момент, передаваемый муфЛ той;L Ref d _c tg ("(. Ip) J where Μ is the moment transmitted by the coupling;

Т_п - усилие всех пружин;T _p - the force of all springs;

R_c - средний радиус кольцевой поверхности трения муфты;R _c is the average radius of the annular friction surface of the coupling;

i = 2 - число плоскостей трения; d_c - средний диаметр рабочей поверхности кулачков;i = 2 is the number of friction planes; d _c is the average diameter of the working surface of the cams;

d - угол подъема рабочей поверхности кулачка по среднему диаметру;d is the angle of elevation of the working surface of the cam on the average diameter;

р - угол трения.p is the angle of friction.

Анализируя формулу (1), замечаем, что при всех прочих равных условиях момент, передаваемый муфтой 'в малой степени зависит от коэффициента трения f.Analyzing the formula (1), we notice that, ceteris paribus, the moment transmitted by the clutch 'to a small extent depends on the friction coefficient f.

При срабатывании ведомая полумуфта A_f нажимной диск 5 с отжимным элементом 9 останавливаются, а ведущая полумуфта 2 и отжимной элемент 8 продолжают вращаться. При этом отжимной элемент 8 винтовой поверхностью давит на винтовую поверхность кулачка отжимного элемента 9- Осевая составляющая усилия, возникающая от передаваемого момента в плоскости контакта кулачков отжимных элементов 8 и 9 противодействует усилию пружин, уменьшая давление, и силу трения между дисками до величины, соответствующей заданному предельному моменту.When triggered, the driven coupling half A _{f, the} pressure disk 5 with the squeezing element 9 stops, and the driving coupling half 2 and the squeezing element 8 continue to rotate. In this case, the squeezing element 8 with a screw surface presses on the screw surface of the cam of the squeezing element 9- The axial component of the force arising from the transmitted moment in the contact plane of the cams of the squeezing elements 8 and 9 counteracts the force of the springs, reducing the pressure and the friction force between the disks to a value corresponding to a given ultimate moment.

Конструкция муфты может найти применение для передачи момента до м_п = 600 кг.см. При больших значение ях заданного М_п следует увеличить число плоскостей трения - i.The design of the coupling can be used to transmit torque up to m _p = 600 kg.cm. For large values of y given M _p should increase the number of friction planes - i.

Предлагаемая конструкция предохранительной муфты повышенной точнос!ти срабатывания позволяет осуществить передачу крутящего момента от вала к звездочке или зубчатому колесу, а также может быть использована для передачи крутящего момента соосными валами, при этом диск-звездочка дол- 5 жен быть соединен соответствующим образом с валом.The proposed design of a safety clutch with increased accuracy allows the transmission of torque from the shaft to the sprocket or gear wheel, and can also be used to transmit torque to the coaxial shafts, while the sprocket disk must be connected to the shaft accordingly.

Предлагаемая муфта смягчает внезапные толчки и удары в начале работы за счет деформации пружин, а затем ’в вследствие скольжения дисков она надежна в работе, применима в широком диапазоне мощностей и обеспечивает высокую точность срабатывания.The proposed clutch softens sudden jolts and shocks at the beginning of work due to the deformation of the springs, and then, due to the sliding of the disks, it is reliable in operation, is applicable in a wide power range and provides high accuracy of operation.

Claims

The invention relates to mechanical engineering and can be used in drives of various machines and mechanisms. Known safety clutch, containing master and slave coupling halves, connected by friction disks, pressed by a pressure disk using adjustable springs, as well as squeezing elements made in the form of barrel-shaped rollers installed in the separator and placed in the radial grooves of the cage, fastened on the stop glass and on the pressure disk 1. A disadvantage of the known clutch is the difficulty of manufacture in connection with performance of the working surfaces of the rollers and clips with high accuracy. The presence of a large number of relative elements significantly complicates the installation of the coupling. I Closest to the proposed is a high-precision friction safety coupling of operation, containing the driven and driving friction coupling halves, the pressure plate, adjustable springs and squeezing elements in the form of a central gear, satellites and right and left threads installed on their shank 12 and 12 J. However, the disadvantages of this coupling are the complexity of the design and installation, low reliability in operation, due to the fact that the assembly of assemblies has a large number of mating parts, difficulty in and The preparation of screw pairs with non-braking multi-thread with a relatively large pitch of the right and left direction. The purpose of the invention is to increase reliability, simplify the design and ease of installation. This goal is achieved by the fact that, for a friction safety clutch of increased accuracy of operation, containing a driven coupling half and a driving coupling half fixed on the drive shaft, a pressure disk, adjustable springs, squeezing elements made with mechanical cams with a working screw surface, one of the squeezing elements is fixed on drive shaft, and the other squeezing element is mounted on the pressure disc. FIG. 1 shows a coupling, a longitudinal section; in fig. 2 shows an end view of a squeezing element attached to a drive shaft; FIG. 3 is a section A-A in FIG. 2; in fig. k - v.id, from the end to the pressing element mounted on the pressure disk; in FIG. 5, section B-B in FIG. H, the Coupling contains a friction half coupling 2 mounted on the drive shaft, fixed on a key 3, a half coupling half in the form of an asterisk, a pressure disk 5, pressed by an adjustable spring 6 installed in the lining disk 5 and a thrust washer 7, squeezing elements 8 and 9 with butt cams. The driven coupling half 4, installed between the driving coupling half .2 and the pressure disk 5, is centered with respect to the shaft by the outer diameter of the squeezing element 8 and the internal diameter of the sleeve 10 along the running fit. The pressure element 9 is mounted on the pressure disk 5 by means of wines-Tau 11. In the pressure hub the disk 5 has fingers 12, which enter freely into the hole of the thrust washer 7 Nut 13 and washer T are located on the thread of the shaft 1. The squeezing element 8 has a working screw surface 15, and the squeezing element 9 has a working screw surface 16. Clutch melts as follows. The movement from the shaft 1 to the asterisk k is transmitted by the frictional forces created along the two friction planes between the pressure disk 5 by the friction coupling half 2 and the asterisk k. The frictional force between the discs at the appropriate moment, transmitted by the asterisk k, is controlled by changing the deformation of the springs b through: your nuts 13 .. V. the period of the torque transmission shaft. 1 with the squeezing element 8 can be rotated relative to all parts of the coupling at a small angle corresponding to the gap between the working surfaces of the cams. The squeezing element 8 transmits the torque point to the sprocket 4 and all the details of the coupling through the squeezing elements 8 and 9. The angle of inclination of the working surfaces is much greater than the friction angle. When assembling and adjusting the clutch, the springs 6 are tightened so that their force is greater than that required for the transmission of a predetermined moment. The excess force of the springs is balanced by the axial component of the force generated by the cams. The moment transmitted by the clutch is determined by the formula: M 2I.L p G1 NC dctg-Cetfp) J where M is the moment transmitted by the clutch; force of all springs; average radius of the annular surface of the friction coupling; - - the number of friction planes; average diameter of the working surface of the cams; the angle of elevation of the cam cam surface over the average diameter; P is the angle of friction. Analyzing formula (1), we note that, for all other equal conditions, the moment transmitted by the clutch depends to a small degree on the coefficient of friction f. When the driven half-coupling kf is actuated, the pressure plate 5 with the squeezing element 3 stops, and the leading coupling half 2 and the squeezing element 8 continue to rotate. At the same time, the squeezing element 8 with a screw surface presses on the screw surface of the cam of the squeezing element 9- The axial force component arising from the transmitted moment in the contact plane of the cams squeezing elements 8 and 9 counteracts the spring force, reducing the pressure and friction force between the discs to the value corresponding to marginal moment. The design of the clutch can be used to transfer the moment to Mr BOO kg.cm. For large values of x given Mp should increase the number of friction planes - i. The proposed design of a safety clutch of enhanced accuracy allows the transfer of torque from the shaft to the sprocket or gear wheel, and can also be used to transfer torque to the axial shafts, and the star disk should be connected properly with the shaft. The proposed coupling relieves sudden shocks and impacts at the beginning of the operation due to the deformation of the springs, and then due to the sliding of the discs, it is reliable in operation, applicable in a wide power range and provides high accuracy of operation. Claims of the invention are a safety clutch of increased accuracy of operation, comprising a driven half coupling and a leading coupling half fixed on the drive shaft, a pressure disc, adjustable springs and squeezing elements, in order to increase reliability, simplify design and convenience of the squeezing elements are made with Ortsov cams with a working screw surface, one of the squeezing elements mounted on the drive shaft. and the other is mounted on a pressure disk. Sources of information should be taken into account when examining N. “The USSR 193857, cl. F 16 D 7/02, .1965.

2. D chenko SK, Kirkach N. f. safety clutches К Гnrvna, the main publishing house of the USSR SSR iteration, 19b2, p. 56. is. 29 (prototype) -.