RU2223425C2 - Vehicle clutch release sleeve - Google Patents

Abstract

FIELD: transport engineering. SUBSTANCE: proposed clutch release sleeve contains radial-thrust ball bearing with rotating outer race and fixed inner race, first bushing on which inner race of bearing is installed, and second bushing nested in first bushing and on which flange is installed. Stop is fitted on second bushing. Stop, first bushing and flange are clamped with interference between opposite end faces of second bushing. First bushing has spherical surface on which inner race of bearing rests through its inner spherical surface. Inner race of bearing is provided with possibility of self-alignment relative to center of sphere. EFFECT: increased service life of clutch sleeve. 2 cl, 2 dwg

Description

 The invention relates to the field of transport engineering and can be used in the construction of clutch devices of vehicles.

 A known design of the clutch engagement clutch [1], including an angular contact ball bearing with a rotating outer ring, a sleeve of elastic material having ribs for self-centering the bearing, a reflective washer rolled on the outer ring of the bearing with an elastic ring mounted between them, a bearing clutch having the sleeve of the coupling is made of synthetic material, and the flanged part of two metal plates embedded in this sleeve is used to transmit axial forces from the clutch control element.

 The disadvantage of this technical solution is the complexity of the design of the bearing clutch due to the presence of two metal parts, which are injection-molded with synthetic material in a mold, which leads to the use of complex and high-precision equipment, reduces the performance of the casting process.

The closest claimed from among the known technical solutions is the clutch of the vehicle [2], containing an angular contact ball bearing with a rotating outer ring and a fixed inner ring, a first sleeve on which the inner bearing ring is mounted, and a second sleeve that goes inside the first bushings, and on which the flange is mounted. The first sleeve has an annular protrusion to prevent axial movement of the bearing relative to it, the second sleeve enters the first sleeve with the formation of a radial clearance, said flange contacts the end surface of the first sleeve, and on the side facing the bearing of the specified end surface of the first sleeve opposite the end of the outer ring of the bearing an annular protrusion and an axially directed board located with a given clearance relative to the outer surface of the outer ring of the bearing, when that the inner and outer surface of the second sleeve in her flange location area delineated in three equal arcs, the radius of which is greater than the radii of the circles bounding said inner and outer surfaces of the sleeve, the arc centers are located in pairs on the bisectors of the central angles of said arcs being equal to 120 ^o , offset from the axis of rotation of the sleeve.

 The disadvantage of this device is its low durability, because due to errors in the manufacture of the coupling parts and its assembly, the load between the balls of the ball bearing is unevenly distributed, the lubricant is poorly held in the bearing, and due to the presence of the bearing weight and friction force between the ends of the inner ring of the bearing and by the highlander of the first sleeve, the bearing is poorly centered with respect to the vehicle coupling element mating with it.

 The objective of the invention is to increase the durability of the coupling.

 The problem is solved in that in the known clutch of a vehicle clutch comprising an angular contact ball bearing with a rotating outer ring and a fixed inner ring, a first sleeve on which an inner bearing ring is mounted, and a second sleeve that goes inside the first sleeve, and of which the flange is mounted, an emphasis, an emphasis are installed on the second sleeve, the first sleeve and the flange are tightened between the opposite ends of the second sleeve, the first sleeve has a spherical surface on which w rests with its spherical inner surface of the inner ring of the bearing with the possibility of self-alignment with respect to center of the sphere, on the inner surface of the outer ring of the bearing washer zapresovana oil deflection and the fence has a protrusion slinger.

 The spherical bearing is located on the inner surface of the bearing and therefore its weight weakly affects the accuracy of centering relative to the mating element of the clutch of the vehicle. Since the bearing is pivotally connected to the surface of the first sleeve, during the operation of the coupling it is able to self-align relative to the working surface of the clutch, as a result of which the load is evenly distributed between the balls and the durability of the coupling increases. This is also facilitated by the presence of an oil shielding plate pressed on the inner surface of the outer ring of the bearing, and an oil seal protrusion on the stop. The oil shielding plate keeps the grease from splashing under the action of centrifugal forces, resulting in reduced wear on the bearing working surfaces and increased durability of the coupling.

 Comparison of the claimed technical solution with the prior art in scientific, technical and patent documentation showed that the set of essential features of the claimed solution was not known earlier, therefore? it meets the condition of patentability “novelty”.

 The proposed solution allows to obtain a new technical effect, therefore, has an inventive step in comparison with the existing level of technology. The proposed technical solution is industrially applicable, as it can be manufactured industrially, efficiently and reproducibly, therefore, it meets the patentability condition “industrial applicability”.

 In FIG. 1 shows a clutch, clutch, longitudinal section; figure 2 - view A.

 The vehicle clutch includes a single row ball bearing, consisting of an inner ring 1, an outer ring 2 and balls 3 separated by a cage 4. The rotating outer bearing ring 2 is in contact with a rotating coupling element (not shown). The non-rotating inner ring 1 is pivotally connected to the first sleeve 5 with the possibility of rotation around the center of the swivel. To do this, on the inner surface of the inner ring 1 of the bearing, near the location of its center of gravity and on the outer surface of the first sleeve 5, spherical surfaces of radius R with a center O located on the axis of the coupling are made (Fig. 1). The first sleeve 5 is mated with a flange 6 with its left end face, and with a stop 7 with its right end face. All of them are mounted on the outer surface of the second sleeve 8 and axially clamped between its flared ends.

 The stop 7 on the side of the outer ring 2 of the bearing has a protrusion, which, on the one hand, limits the axial movement of the inner ring 1 of the bearing, on the other hand, creates the necessary tightness of the inner cavity of the bearing. The inclination of the surface of the protrusion towards the inner ring provides the lubricant from below to the contacting spherical surfaces of parts 1 and 5. On the opposite side of the bearing, its tightness is ensured by a labyrinth seal 9 and an oil deflector washer 10. A double labyrinth seal prevents contaminants from entering from outside, the oil reflector washer 10 reliably protects splashing grease from the bearing cavity under the action of centrifugal forces during the operation of the coupling. Part of the lubricant through the gap between the inner ring 1 and the oil washer 10 gets to the articulation of parts 1 and 5, providing ease of articulation and preventing wear of the mating surfaces.

 The flange 6 from the side of the bearing has four protrusions (Figs. 1 and 2), along which the labyrinth seal 9 is centered and which enters the corresponding radial grooves of the inner ring 1 of the bearing, holding it from possible rotation around the axis under the influence of coupling vibrations during operation.

 The assembly of the coupling is carried out in the following sequence. The bearings are pre-assembled by interconnecting the inner ring 1, the outer ring 2 and the balls 3 with a cage 4. Grease is placed in the bearing. A reflective washer 10 is pressed into the inner ring 2. Then, on the second sleeve 8 previously flared from the outer ring of the bearing, the stop 7 is mounted in series, the previously assembled bearing, the first sleeve 5, the labyrinth seal 9 and the flange 6. After that, the second sleeve is flared from the flange 6 side creating interference between parts 7, 5 and 6.

 The operation of the device is as follows. When installing the clutch in the assembly on a cylindrical guide (not shown) through the hole of the second sleeve 8, an axial force is applied to the flange 6 from the clutch engagement fork (not shown). Under the action of the fork, the clutch moves along the guide, acting on the rotating clutch element (not shown) by the outer ring 2 of the bearing, thereby disengaging the clutch.

где α - угол контакта внутреннего кольца сферических поверхностей внутреннего кольца 1 подшипника и первой втулки 5, отсчитанный от плоскости, перпендикулярной оси муфты (фиг.1);
f - коэффициент трения скольжения контактирующих поверхностей;
R - радиус сферы;
do - диаметр полоски контакта наружного кольца 2 подшипника с вращающимся элементом сцепления.Since the ball bearing in the coupling is mounted on a hinge, with the hinge approximately located at the center of gravity of the bearing, the bearing is easily centered relative to the rotary clutch (not shown), the bearing weight does not affect this, and the load is evenly distributed between the balls. This ensures high durability of the coupling. The friction force in the contact zone of parts 1 and 5 can interfere with self-centering of the bearing. This influence of the friction force is eliminated by providing the following relationship between the dimensions of the coupling parts:

where α is the contact angle of the inner ring of the spherical surfaces of the inner ring 1 of the bearing and the first sleeve 5, counted from the plane perpendicular to the axis of the coupling (figure 1);
f is the coefficient of sliding friction of the contacting surfaces;
R is the radius of the sphere;
do - the diameter of the contact strip of the outer ring 2 of the bearing with a rotating clutch.

 Technical and economic efficiency of the invention is as follows.

 1. Increases the durability and reliability of the clutch.

 2. The design of the coupling is simplified and the cost of its manufacture is reduced.

Sources of information
1. Application of France 263694, cl. F 16 D 23/14, 1990.

 2. RF patent 2115042 C1, cl. 6 F 16 D 23/14 // Novikov A.F., Shnyr S.M., Zhavoronkov E.V.

Claims (1)

A vehicle engagement clutch comprising an angular contact ball bearing with a rotating outer ring and a non-rotating inner ring, a first sleeve on which the bearing inner ring is mounted, and a second sleeve that is included inside the first sleeve and on which a flange is installed, characterized in that the second sleeve has an abutment, an abutment, the first sleeve and the flange are tightened between the opposite ends of the second sleeve, the first sleeve has a spherical surface on which it relies on its inside its inner spherical surface of the bearing ring with the possibility of self-alignment with respect to center of the sphere, the outer ring of the bearing on the inner surface of the pressed oil deflection washer and the fence has a protrusion slinger.

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